A self-aligning bearing

Abstract: A self-aligning bearing for a 0.5kW PMDC electric motor has a bearing member (1) having a cylindrical inner surface (2) for receiving a rotatable shaft and an outer surface comprising a first external, part-spherical, surface-of-revolution (3) and a second external surface-of-revolution (4, 5) comprising a first part (4) extending inwardly from the first external, part-spherical, surface-of-revolution (3) and a cylindrical second part (5) extending from the first part (4). A housing (6) has a convergent end (7) defining an internal surface of revolution (8) which engages the first external, part-spherical, surface-of-revolution (3) and encloses a retainer (9) engaging the first part (4) of the second external surface-of-revolution (4, 5). The housing (6) also encloses a support ring (11) which holds the retainer (9) in place and has a radially inner part (12) which surrounds the second part (5) of the second external surface-of-revolution (4, 5) with a clearance space (13). The support ring (11) thereby limits tilting movement of the bearing member (1) about axes perpendicular to the axis of the bearing member (1).

Description: Field of the Invention The invention relates to self-aligning bearings and in particular, although not exclusively, to self-aligning bearings for small electric motors of up to 0.5kW capacity. Background Art To accommodate imperfections in the manufacture of small electric motors, at least one of the two shaft bearings is normally a self-aligning bearing. This ensures that the rotor can rotate freely even when the two bearings are not co-axially aligned. A self-aligning bearing such as this normally comprises a bearing member, a housing enclosing the bearing member and a resilient retainer which holds the bearing member in the housing while, at the same time, allowing the bearing member to tilt or swivel within the housing. The bearing member has a cylindrical inner surface, for receiving a rotatable shaft, and a single part-spherical surface-of- revolution forming the whole of the outer surface of the bearing member. Opposite ends of this outer surface are supported by a convergent end of the housing and by the resilient retainer. Radial loading on the bearing members of self-aligning bearings for larger electric motors may be adequately supported by the convergent end of the housing and by a relatively robust resilient retainer. Moreover, axial clearances can be limited to such an extent that axial movement and, therefore, simultaneous radial movement are sufficiently restricted to prevent overstraining of the retainer. However, in self-aligning bearings for smaller electric motors, the retainers are much more flimsy and, although axial clearances can be somewhat reduced, they permit much greater movement relative to the size of the components and it is much more likely that the retainers will be damaged in such a way as to be incapable of the holding the bearing member in place. Small electric motors of up to 0.5kW capacity, which can be handled manually, are particularly prone to this type of damage because they can be easily dropped in such a way as to be subjected to shock loading. It is therefore necessary to limit radial movement of the bearing member. This can be done by providing the housing with a part- spherical seat which engages the part-spherical surface-of-revolution on the outer surface of the bearing member and which contains a circular region which defines a plane, perpendicular to the axis of the housing, which contains the centre of curvature of the part-spherical seat. However, formation of a part-spherical seat is relatively costly and this solution precludes the use of a simple frusto-conical seat. It is therefore more usual to provide a support ring which is supported within the housing and has an inner portion surrounding the bearing member with an annular clearance space between the support ring and the bearing member for limiting radial movement of the bearing member. It is therefore known to provide a self-aligning bearing such as this in which a bearing member has an inner surface, for receiving a rotatable shaft, and an outer surface comprising a first external, part-spherical, surface-of-revolution, formed around the axis of the bearing member; a housing for accommodating the bearing member has a convergent end defining an internal surface- of-revolution engaging the first external, part-spherical, surface-of-revolution to provide the bearing member with both radial and axial support; a retainer is supported within the housing and has resilient means engaging the bearing member so as to urge the first external, part- spherical, surface-of-revolution axially into engagement with the convergent end of the housing; and a support ring has a radially inner portion surrounding the bearing member with an annular clearance space between the support ring and the bearing member for limiting radial movement of the bearing member. A self-aligning bearing of either construction permits the bearing member, or any shaft supported within the bearing member, to be tilted or swivelled extensively, for example: through an angle of 30°, about an axis perpendicular to the axis of the bearing member. However, in use, it is only necessary for the bearing member to be capable of the tilting or swivelling through an angle of the order of 1°. A prior art arrangement according to the preamble of claim 1, in which in use tilting movement is limited, is shown in FR-A-965759 in which a cylindrical sleeve bearing is provided with a part-spherical shoulder which bears against a correspondingly shaped end of a bearing housing formed in the motor end flange. A bearing retainer in the form of a resilient washer bears against the shoulder to urge it into contact with the housing. A cover surrounds the housing, retainer and bearing and accommodates greasing felts providing an oil reservoir for the bearing, and limits radial movement of the bearing sleeve when a shaft is inserted therein. However there are situations in which it is disadvantageous if the bearing member is capable of tilting or swivelling movement permitted by known designs. Thus, in the assembly of small electric motors, particularly by automated processes, difficulty is encountered when the bearing member is excessively inclined to the axis of the housing because it is necessary to pass the rotor axially through the stator and, in this case, it is impossible to pass the shaft of the electric motor through the bearing member until the bearing member has been substantially aligned with the axis of the bearing housing and the remainder of the motor stator. Similarly, when the shaft of the electric motor has been inserted into the bearing member, it is often necessary to manipulate the part-assembled motor before the other end of the motor shaft is located in a second motor bearing. In this case, it is important to limit tilting or swivelling movement of the motor shaft so as to prevent the motor armature mounted on the shaft from fouling the motor stator. This also applies where it is necessary to transport the part-assembled motor before the second motor bearing is fitted. Disclosure of the Invention It is the purpose of the present invention to provide a self-aligning bearing in which the disadvantages of known constructions are at least reduced. It is thus an object of the present invention to provide a self-aligning bearing in which the construction is modified specifically to limit the extent of self-alignment. According to the invention, this is achieved by providing a support ring fixed with respect to the housing and having a radially inner portion which surrounds the second portion of the second external surface with a clearance space to limit radial movement of the bearing member, both before and after the rotatable shaft is inserted into the bearing member. Thus, according to the invention, there is provided a self aligning bearing comprising a bearing member having an inner surface for receiving a rotatable shaft, and an outer surface, the outer surface comprising a first external surface -of-revolution being part-spherical and formed around the axis of the bearing member, and a second external surface of revolution formed around the axis of the bearing member being non-coextensive with any imaginary spherical surface having the same centre as the first external surface-of-revolution, and having a first portion which extends substantially transversely of the axis of the bearing member and intersects the first external surface-of-revolution, and a second portion which extends substantially axially; a housing for accommodating the bearing member, having a convergent end which defines an internal surface-of-revolution which engages the first external surface-of-revolution to provide the bearing member with both radial and axial support; and a retainer having resilient means and being supported within the housing with the resilient means engaging the first portion of the second external surface-of-revolution so as to urge the first external surface-of-revolution axially into engagement with the convergent end of the housing characterised by a support ring fixed with respect to the housing and having a radially inner portion surrounding the second portion of the second external surface-of-revolution with an annular clearance space between the support ring and the second portion to limit radial movement of the bearing member both before and after the rotatable shaft is inserted into the bearing member. As the second external surface-of-revolution faces the inner portion of the support ring across a clearance space or small gap when the bearing element is in the neutral position, the second portion forms (constitutes) an abutment surface which engages the support ring to limit tilting or swivelling of the bearing member as a result of sliding movement between the bearing element and the housing. This sliding movement is translated to the second portion as radial movement as the bearing element pivots about an axis perpendicular to the axis of the bearing element and it is this radial movement which is limited by the bearing element abutting the support ring. This radial movement is accommodated by the deformation of the resilient retainer means. The support ring provided to restrict tilting or swivelling movement of the bearing member relative to the housing, in accordance with the invention, is therefore able to serve the important secondary function of preventing overstraining of the retainers of self-aligning bearings for small electric motors. The first portion of the second external surface-of revolution preferably extends inwards from the first external, part-spherical, surface-of-revolution. The retainer can then be mounted adjacent the convergent end of the housing for engagement with this first portion so that, when necessary, an axially short housing can be provided. This is desirable in some cases where space is limited. Where the support ring also holds the retainer in position, the housing need only be long enough to accommodate the retainer and the outer portion of the support ring. In a preferred embodiment of the invention, the first portion of the second external surface has inner and outer edges and the second portion of the second external surface extends from the inner edge of the first portion. This provides a bearing member having much less volume than a traditional bearing member in which the whole of the outer surface constitutes a single part-spherical surface. This not only saves weight and material, but where the bearing member is of porous, sintered construction, for impregnation with lubricating oil, this oil is much more rapidly available at the inner and outer surfaces of the bearing member. Thus, as the bearing member cools, on cessation of operation, oil is withdrawn into the inner core of the cross-section of the bearing member. When use of the bearing member is recommenced, frictional heat warms the oil which travels by capillary action from the central core of the cross-section of the bearing member to the inner and outer surfaces and, as these inner and outer surfaces are now much closer to the central core, the time taken to provide lubrication at the inner and outer surfaces is reduced. The second portion of the second external surface-of- revolution is preferably cylindrical in shape. This not only simplifies construction of the bearing member, it also simplifies mounting of the support ring which, in this case, can be disposed at any point along the length of the cylindrical second portion of the second external surface-of-revolution. According to a further preferred feature of the invention, the support ring has a radially outer portion in fixed engagement with the housing and an axially extending wall surrounding and radially spaced from the second external surface-of-revolution between the radially inner and outer portions of the support ring whereby the radially outer portion is axially offset from the radially inner portion towards the retainer. The resultant increase in the axial distance between the radially inner portion of the support ring and the axis, perpendicular to the axis of the bearing member, about which the bearing member is able to tilt or swivel ensures that this tilting or swivelling movement can be severely restricted even though the radial clearance between the support ring and the second external surface-of-revolution is relatively large. A further advantage of this form of construction is that a pad of oil absorbent material may be seated between the second portion of the second external surface-of-revolution and the axially extending wall of the support ring. This pad may consist of a single length of felt, of substantially rectangular cross-section, extending 360° around the second external surface-of-revolution. Alternatively, the pad may consist of several turns of felt tape which together provide a substantially rectangular cross-section. Where the bearing member is of porous, sintered construction and is impregnated with lubricating oil, the pad serves to absorb any excess oil released from the bearing member and any oil retained by the pad is available for lubrication on depletion of the oil originally provided within the bearing member. Alternatively, where the bearing member is not impregnated with a supply of lubricating oil, but is porous or provided with oil supply passages, the pad itself can serve as a reservoir for this oil. In known self-aligning bearings, the retainer normally comprises an annular outer portion, extending inwardly from one end of a short mounting sleeve, and a plurality of resilient fingers projecting radially inwards of the annular outer portion. Retainers such as this serve quite adequately in self-aligning bearings according to the present invention and can be easily clamped in position between an end portion of the housing and the support ring. As an alternative, to simplify construction and to reduce the necessary length of the housing, the mounting sleeve can be omitted. In this case, the outer annular portion of the retainer may be clamped between the end portion of the housing and the support ring. A totally different type of retainer, of simpler construction, may be provided in the form of a length of elastomeric material which surrounds the second external surface-of-revolution and is held in place by the support ring. This length of elastomeric material may constitute a closed loop or a single length wrapped once around the second external surface-of-revolution and is preferably of circular cross-section. In this case, the part of the length of elastomeric material which abuts the first portion of the second external surface-of-revolution constitutes the resilient means which urge the first external, part- spherical, surface-of-revolution axially into engagement with the convergent end of the housing. As a further variation for a self-aligning bearing in a very small electric motor, regardless of the type of retainer used, the resilient means on one side of the retainer may be stiffer than the resilient means on the diagonally opposite side. As a result, the bearing member is swivelled or tilted until the second external surface of revolution abuts the inner portion of the support ring. Moreover, when the motor shaft is inserted in the bearing member, the difference in the stiffness of the resilient means can be arranged so as to ensure that the axis of the bearing member is inclined to the axis of the motor shaft to thereby reduce the effective clearance between the bearing member and the motor shaft. This reduces noise during operation of the motor. A prior art construction and five embodiments of the invention are hereinafter described, by way of example only with reference to the accompanying drawings. Brief Description of the Drawings Figure 1 is a sectional side elevation of a known self- aligning bearing for a 0.5kW PMDC electric motor; Figure 2 is a sectional side elevation of a self-aligning bearing according to the invention, for a similar sized PMDC electric motor; Figures 3 and 4 are a sectional side elevation and an end elevation of retainers for use in the self-aligning bearings shown in Figures 1 and 2; Figures 5 and 6 are a sectional side elevation and an end elevation of a modified form of the retainer shown in Figures 3 and 4; Figures 7 to 9 are sectional side elevations of self- aligning bearings according to the invention and incorporating modified retainers as shown in Figures 5 and 6; Figure 10 is a schematic sectional side elevation of a further self-aligning bearing according to the invention and incorporating a different form of retainer; and Figures 11 and 12 are a sectional side elevation and an end elevation of a modified form of the retainer shown in Figures 5 and 6. Detailed Description of the Preferred Embodiments In the known self-aligning bearing shown in Figure 1, a bearing member 1 has a cylindrical inner surface 2, for receiving a rotatable shaft (not shown), and an outer surface 3 comprising a part-spherical surface-of- revolution formed around the axis of the bearing member 1. The bearing member 1 is mounted in a housing 6 which has a frusto-conical convergent end 7 engaging the outer surface 3 of the bearing member 1. A retainer 9, shown in detail in Figures 3 and 4, has resilient fingers 10 which bear against the opposite sides of the outer surface 3 of the bearing member 1 so as to urge the bearing member 1 axially into engagement with the frusto-conical convergent end 7 of the housing 6. The bearing member 1 is thus capable of substantial tilting or swivelling movement about axis perpendicular to the axis of the bearing member 1 and this can cause difficulty when inserting the motor shaft within the bearing member 1, particularly in an automated assembly process. This known construction also has the added disadvantage that, although axial movement of the bearing member 1 is constrained to some extent by abutment with the motor shaft, the retainer 9 is too flimsy to prevent combined axial and radial movement of the bearing member 1 under shock loading as, for example, when a motor containing the self-aligning bearing is dropped from a height of one metre. In fact, if the retainer 9 was subjected to shock loading of this nature, it would be permanently distorted to such an extent that it could no longer serve its required function of urging the bearing member 1 axially towards the frusto-conical convergent end 7 of the housing 6. To avoid this form of damage, a support ring 11 is mounted between the frusto-conical convergent end 7 of the housing 6 and the retainer 9. An inner portion 12 of the support ring 11 surrounds the bearing member 1 in such a way that a small annular clearance space 13 is left between the outer surface 3 of the bearing member 1 and the inner portion 12 of the support ring 11. The support ring 11 thereby limits radial and concomitant axial movement of the bearing member 1 so that the resilient fingers 10 of the retainer 9 are never overstrained. The retainer 9 is made from spring steel and, as shown in Figures 3 and 4, has eight resilient fingers 10 projecting radially inwards from an annular outer portion 19 extending from one end of a short mounting sleeve 20. As shown in Figure 4, individual fingers 10 are separated by slots 21 extending from small apertures 22 formed in the annular outer portion 19 of the retainer 9. As shown in Figure 1, the outer portion 19 and the mounting sleeve 20 of the retainer 9 are seated, respectively, against the support ring 11 and the inner surface of the housing 6. Although not shown, means are provided for holding the retainer 9 and the support ring 11 in their correct positions. Thus, the retainer 9 may be attached to the support ring 11 and the support ring 11 may be attached to the housing 6. In the self-aligning bearing according to the present invention, as shown in Figure 2, the bearing member 1 is modified in such a way that, in addition to a first external, part-spherical, surface-of-revolution 3, the outer surface of the bearing member 1 has a second external surface-of-revolution about the axis of the bearing member 1 having a frusto-conical first portion 4 and a cylindrical second portion 5. The frusto-conical first portion 4 has inner and outer edges 14 and 15 and the second cylindrical portion 5 extends from the inner edge 14 ofthe frusto-conical first portion 4. As in the prior art construction illustrated in Figure 1, the first external, part-spherical, surface-of-revolution 3 engages a frusto- conical internal surface-of-revolution 8 defined by the convergent end 7 of the bearing housing 6 and, to this extent, the bearing member 1 is again capable of substantial tilting or swivelling movement about axes perpendicular to the axis of the bearing member 1. However, as shown in Figure 2, the second external surface-of-revolution having portions 4 and 5 does not coincide (and is therefore not coextensive) with any imaginary spherical surface having the same centre as the first external, part-spherical, surface-of-revolution 3. This ensures that, on tilting or swivelling movement of the bearing member 1, the first and second portions 4 and 5 of the second external surface-of-revolution move radially with respect to such an imaginary spherical surface. As shown, the retainer 9 is seated within the housing 6 adjacent the convergent end 7 so that the resilient fingers 10 bear against the first portion 4 of the second external surface-of-revolution between the inner and outer edges 14 and 15. As shown in Figure 2, a retainer 9 similar to the retainer 9 shown in Figure 1 is clamped in place by means of the support ring 11 which has a radially outer mounting sleeve portion 23 in frictional engagement with the inner surface of the housing 6. As shown, the support ring 11 has a radially inner portion 12 surrounding the cylindrical second portion 5 of the second external surface- of-revolution 4, 5. The annular clearance space 13 between the radially inner portion 12 of the support ring 11 and the bearing member 1 not only limits radial and concomitant axial movement of the bearing member 1, as in the case of the known self- aligning bearing shown in Figure 1, it also limits the extent to which the bearing member 1 is able to rotate about an axis perpendicular to the axis of the bearing member 1 as a result of self-aligning movement between the first external, part-spherical, surface-of-revolution 3 and the frusto-conical internal surface-of-revolution 8 defined by the convergent end 7 of the housing 6. One secondary advantage of the construction shown in Figure 2 is that the axial length of the housing 6 may be less than that required in the construction shown in Figure 1. This is because the retainer 9 is arranged to bear against the bearing member 1 through the first portion 4 of the second external surface-of-revolution 4, 5 which is much closer to the frusto-conical convergent end 7 of the housing 6. As shown, the retainer 9 is clamped in position by the support ring 11. However, it would be possible to replace the retainer 9 in Figure 2 with a smaller retainer 9 having the same dimensions as the retainer 9 shown in Figure 1. In this case, the retainer 9 would not be clamped between the support ring 11 and the housing 6, but merely supported by the support ring 11 so as to bear against the first portion 4 of the second external surface. This would facilitate assembly by allowing the retainer 9 to centre itself on the first portion 4. To further reduce the axial length of the housing 6, it is possible to modify the retainer 9, as shown in Figures 5 and 6, by omitting the mounting sleeve 20 provided on the conventional retainer shown in Figures 3 and 4. In this case, the outer annular portion 19 of the retainer 9 may be clamped between the housing 6, adjacent the frusto-conical convergent end 7, and the support ring 11, as shown in Figure 7, or merely supported by the support ring 11, as shown in Figures 8 and 9. In each of these constructions, the support ring 11 is provided with an axially extending wall 17 which is radially spaced from the second external surface-of-revolution 4, 5 between radially inner and outer portions 12 and 16. As a result, the radially outer portion 16 of the support ring 11 is axially offset from the radially inner portion 12 towards the retainer 9. In the construction shown in Figure 7, this offset is quite small and so it is possible to provide a housing 6 of very restricted axial length. However, in the construction illustrated in Figures 8 and 9, the axial offset is more substantial. This ensures that the extent of tilting or swivelling movement of the bearing member 1 about an axis perpendicular to an axis of the bearing member 1 can be limited to small angles without relying on very small annular clearance spaces 13, between the inner portion 12 of the support ring 11 and the bearing member 1. Although this involves some axial increase in the length of the housing 6, the space between the axially extending wall 17 of the support ring 11 and the bearing member 1 can be utilized, as shown in Figure 9, to hold a felt pad 18. Where the bearing member 1 is of porous, sintered construction and is impregnated with lubricating oil, the pad 18 serves to absorb any excess oil released from the bearing member 1. Alternatively, the pad 18 may be impregnated with lubricating oil to serve as a reservoir. Assembly is facilitated by first fitting a pad 18 of felt material within the support ring 11 and then passing the cylindrical second portion 5 of the second external surface forming part of the outer surface 3 of the bearing member 1 through the retainer 9, the pad 18 and the inner portion 12 of the support ring 11. The felt material may be in the form of closed loop, a single strip extending 360° around the support ring 10, or a number of helically or spirally wound layers. The embodiments described with reference to Figures 2 and 7 to 9 incorporate retainers 9 as described with reference to Figures 3 to 6, in which the resilient fingers 10 all exert the same axial force on the bearing member 1. However, for very small electric motors in which the retainer 9 is clamped between the support ring 11 and the housing 6, as shown in Figures 2 and 7, the retainer 9 may be formed, as shown in Figures 11 and 12, with the resilient fingers 10A on one side of the retainer 9 formed wider and therefore stiffer than the resilient fingers 10B on the other side of the retainer. In this case, the difference in stiffness causes the bearing member to be swivelled or tilted, in a clockwise direction as shown in Figures 2 and 7, until the second portion 5 of the second external surface abuts the inner portion 12 of the support ring 11. Moreover, the difference in stiffness can be chosen so that, regardless of the orientation of the motor shaft mounted in the bearing member to the axis of the housing, the axis of the bearing member 1 is always inclined to the axis of the shaft. This reduces the effective clearance between the shaft and the inner surface 2 of the bearing member 1 and results in a much quieter operation of the electric motor. Although the difference in width and, therefore, stiffness between the fingers 10A and 10B has been achieved by reducing the angular spacing of the slots 21 between the narrower fingers 10B, a similar effect can be achieved with equiangularly spaced slots 21 by either increasing the width or the length of the slots 21 between the less stiff fingers 10B. In the construction shown in Figure 10, the support ring 11 has an outer support sleeve 23 in frictional engagement with the inner surface of the housing 6. Besides limiting radial and concomitant axial movement of the bearing member 1 and tilting or swivelling movement of the bearing member 1, the support ring 11 also holds a retainer 9, in the form of a rubber loop in engagement with the first portion 4 of the second external surface of the bearing element so as to urge the first external, part-spherical surface-of- revolution 3 axially into engagement with the frusto-conical internal surface-of-revolution 8 defined by the convergent portion 7 of the housing 6. As shown in Figure 10, the rubber ring forming the retainer 9 is originally of circular cross-section and so is compacted and deformed when locked in position, even though for the sake of clarity, this has not be shown in Figure 10. It is clear, however, that the portion of the rubber loop adjacent the first portion 4 of the second external surface-of-revolution 4, 5 constitutes resilient means 10 which operate in the same manner as the resilient fingers of the retainer 9 shown in Figures 3 to 6. To provide a difference in the stiffness of the resilient means 10 on opposite sides of a retainer 9 similar to that provided by use of the retainer 9 shown in Figures 11 and 12, the rubber ring may be replaced by two half rings of rubber of different compressive stiffness. Alternatively, the cross-section of one half ring may be larger than the cross-section of the other half ring.

Claims: A self aligning bearing comprising: a bearing member (1) having an inner surface (2) for receiving a rotatable shaft, and an outer surface, the outer surface comprising a first external surface-of-revolution (3) being part-spherical and formed around the axis of the bearing member (1), and a second external surface-of-revolution formed around the axis of the bearing member being non-coextensive with any imaginary spherical surface having the same centre as the first external surface-of-revolution, and having a first portion (4) which extends substantially transversely of the axis of the bearing member (1) and intersects the first external surface-of-revolution, and a second portion (5) which extends substantially axially, a housing (6) for accommodating the bearing member (1), having a convergent end (7) which defines an internal surface-of-revolution (8) which engages the first external surface-of-revolution (3) to provide the bearing member (1) with both radial and axial support; and a retainer (9) having resilient means (10), and being supported within the housing with the resilient means (10) engaging the first portion (4) of the second external surface-of-revolution so as to urge the first external surface-of-revolution axially into engagement with the convergent end (7) of the housing (6) characterised by: a support ring (11) fixed with respect to the housing (6) and having a radially inner portion (12) surrounding the second portion (5) of the second external surface-of-revolution with an annular clearance space between the support ring and the second portion (5) to limit radial movement ofthe bearing member (1) both before and after the rotatable shaft is inserted into the bearing member (1). A bearing, according to Claim 1, in which the first portion (4) of the second external surface extends radially inwards from the first external surface. A bearing, according to Claim 2, in which the first portion (4) of the second external surface has inner and outer edges (14 and 15) and the second portion (5) of the second external surface extends from the inner edge (14) of the first portion (4). A bearing, according to Claim 3, in which the second portion (5) of the second external surface is a cylindrical surface. A bearing, according to any of the preceding claims, in which the support ring (11) has a radially outer portion (16) supported in fixed relation to the housing (6) and an axially extending wall (17) surrounding and radially spaced from the second portion (5) of the second external surface between the radially inner and outer portions (12 and 16) of the support ring (11) whereby the radially outer portion (16) is axially offset from the radially inner portion (12) towards the retainer (9). A bearing, according to Claim 5, in which a pad (18) of oil absorbent material is seated between the second portion (5) of the second external surface-of-revolution (4, 5) and the axially extending wall (17) ofthe support ring (11). A bearing, according to any one of the preceding claims, in which the retainer (9) is supported in fixed relation to the housing (6) by the support ring (11). A bearing, according to any one of the preceding claims, in which the retainer (9) comprises an annular outer portion (19) and the resilient means (10) comprises a plurality of resilient fingers projecting radially inwards from the annular outer portion (19). A bearing, according to any one of claims 1 to 5, in which the retainer (9) is a length of elastomeric material which surrounds the second portion (5) and bears against the first portion (4) of the second external surface-of-revolution. A bearing, according to any one of Claims 7 to 9, in which the resilient means (10A) on one side of the retainer (9) are stiffer than the resilient means (10B) on the diagonally opposite side.

Inventors: STROBL GEORG, STROBL, GEORG
Applicants: JOHNSON ELECTRIC SA, JOHNSON ELECTRIC S.A.
Application year: 1992
Main classification: F16C23
IPC codes: H02K5, F16C23