BEARING WITH ROLLING BALL SEPARATOR

Abstract: A ball bearing includes an outer ring (14) having a rotation axis (12) and an inner ring (16), which rotates relative to the outer ring, and a plurality of bearing balls (18 to 32) disposed between the outer ring and the inner ring. A plurality of rollers (34 to 48) are peripherally disposed between the bearing balls and are radially disposed between the outer ring and the inner ring. First and second axially spaced tracks (52, 56) are disposed on opposite sides of the bearing balls for supporting the rollers. First and second plates (50, 54), which support the first and second tracks (52, 56), are connected to and supported by the inner ring (16). The bearing balls and roller portions have respective radial dimensions, and the outer ring and inner ring and roller tracks have respective radial dimensions in order to provide substantially pure rolling friction, without any sliding friction.

Description: The invention relates to ball bearings having ball separators. The prior art ball bearing includes an outer ring having an axis, an inner ring rotatable relative to the outer ring about the axis, a plurality of bearing balls, and a cage separator with respective pockets for the bearing balls. A problem with the prior art ball bearing is that there is a relatively large sliding friction at the interface of each bearing ball and the cage which causes a relatively large bearing torque. U.S. Patent 4,372,633 describes a substantially zero friction electrical conductor assembly and provides a concept of eliminating sliding friction by using substantially pure rolling friction at the interfaces of its parts. It is an object of the invention to reduce friction between the balls or other rolling members of a ball bearing and the ball separator. This is achieved by the invention as characterized in claim 1. Preferred embodiments are described in the dependent claims. According to the present invention, a ball bearing includes an outer ring having an axis, an inner ring rotatable relative to the outer ring about the axis, a plurality of bearing balls radially disposed between the rings, a plurality of roller separators peripherally disposed between the bearing balls, and a pair of tracks for supporting the roller separators. By using the plurality of roller separators peripherally disposed between the bearing balls and by using the pair of tracks for supporting the roller separators, instead of the cage separator, sliding friction and its bearing torque can be minimized. Also, the concept of substantially pure rolling friction at the interfaces of its parts can be applied. The above advantages and subsequent description will be more readily understood by reference to the following description of a preferred embodiment of the invention shown in the drawings, wherein: Fig. 1 is a vertical section view of a bearing according to the invention as taken along the line 1-1 of Fig. 2; Fig. 2 is a section view as taken along the line 2-2 of Fig. 1; Fig. 3 is a schematic view of a portion of Fig. 1 as taken along the line 3-3 of Fig. 2; Fig. 4 is a schematic section view along the line 4-4 of Fig. 2; and Fig. 5 is an alternate section view similar to Fig. 4. In Fig. 1, a ball bearing 10 is shown. Bearing 10, which has a rotation axis 12, includes an outer ring or race 14 and an inner ring or race 16. Bearing 10 also includes a plurality of identical bearing balls 18, 20, 22, 24, 26, 28, 30, 32, which are disposed between outer ring 14 and inner ring 16 in a radial direction. Bearing 10 also includes a plurality of identical rolling elements, or roller separators, or rollers 34, 36, 38, 40, 42, 44, 46, 48, which are alternately disposed between bearing balls 18, 20, 22, 24, 26, 28, 30, 32, in a peripheral direction. In Fig. 2, inner ring 16 has a left side plate 50, which is fixedly connected thereto. Plate 50 has a ring-shaped roller track 52, which is integral therewith. Inner ring 16 also has a right side plate 54, which is fixedly connected thereto. Plate 54 has a ring-shaped roller track 56, which is integral therewith. In Fig. 2, roller 42, which is a typical roller, has a left cylindrical portion 58, a right cylindrical portion 60, and a recessed center portion 62. In Fig. 4, the radius 64 of recessed center portion 62 of typical roller 42 is slightly larger than the radius 66 of typical bearing ball 26, as explained hereafter. In Fig. 3, which is a schematic view of a portion of Fig. 1, the component dimensional relationships are shown. In Fig. 2, track 52 has a radially inner rolling surface 68 on which left cylindrical portion 58 rolls, and has a radially inner rolling surface 70 on which right cylindrical portion 60 rolls. In Figs. 1 and 2, typical roller 42 is located by contacts with two adjacent balls 26, 28 along its center portion 62, and with tracks 52, 56 at respective left portion 58 and right portion 60. By appropriate selection of track and roller diameters, it is possible to design a bearing in which there is pure rolling at each point of relative motion. Since rolling interfaces have less friction and wear than sliding interfaces, in general, the overall drag torque of bearing 10 is minimized. In Fig. 3, the dimensions of typical bearing balls 18, 20 and rollers 34, 36 and track surface 68 are shown. The following equations 1 and 2 may be immediately derived from the geometric relationships represented in Fig. 3. Equation 3 is derived from matching velocities at containing interfaces, to insure pure rolling. Where: R T = radius of the roller track R I = radius of the inner race R B = radius of the ball R R = radius of the roller at the point of contact between the roller and the ball R A = radius of the roller at the point of contact between the roller and the roller track ϑ = angle between bearing radii that intersect ball and roller centers, where N = number of balls β = the complement of the angle between the line connecting the centers of the ball and roller, and the line connecting the centers of the ball and inner ring All of the independent parameters (R T , R I , R B , R R , R A and ϑ) may be manipulated using the relationships of equations 1, 2 and 3, but in practice there are often constraints on some of the parameters. A common example would have values for R I , R B , R T and ϑ given. In this case the unknowns are R R and R A . Equations 4 and 5 are expressions for R R and R A , derived from equations 1, 2 and 3. In Figs. 4 and 5, the design of roller 42, which is a typical roller, is important to assure alignment stability during operation. In order to assure that roller 42 does not slide axially and maintains its longitudinal axis 74 parallel to the rotational axis 12 of the bearing 10, radius 64 is machined into roller 42 that is only slightly larger than that radius 66 of ball 26 it is rolling on. Fig. 4 shows a typical roller 42 contact with an adjacent ball 26. Note that this cut-away view in Fig. 4 is in the plane that passes through the ball center 72 and roller center 74. The radius of curvature 64 of roller 42 is generally 52 to 55% of the ball diameter. The effect of this intimacy between the ball and roller is that if a disturbing force is applied to the roller, such as a might be caused by a piece of debris on the roller track, a restoring force, opposing the disturbance, will be generated between the ball and the roller. Fig. 5 illustrates the generation of a restoring moment to roller 42 that has been angularly displaced, as it might from encountering a retarding force at one of the two track contacts. The ball/roller contact forces F C form a restoring moment since they no longer act along the line of centers. In this way, the invention provides separation and relative positioning for the rollers and bearing balls in bearing 10. This separation is accomplished with small rollers 34, 36, 38, 40, 42, 44, 46, 48, whose center portions 62 roll on adjacent bearing balls 18, 20, 22, 24, 26, 28, 30, 32, contacting them outside the pitch diameter, while their left end portions 58 and right end portions 60, which are different in diameter from center portion 62, roll on respective surfaces 68, 70 of tracks 52, 56. Bearing 10 provides pure rolling at all interfaces, so that drag torque is minimized. As specified in the aforementioned equation 3, matching velocities are provided at all contacting interfaces, to insure pure rolling and to avoid sliding friction. While the invention has been described in its preferred embodiments, it is to be understood that the words which have been used are words of description rather than limitation and that changes may be made within the purview of the appended claims without departing from the true scope and spirit of the invention in its broader aspects. For example, rollers 34, 36, 38, 40, 42, 44, 46, 48, may be located inside the pitch diameter of bearing balls 18, 20, 22, 24, 26, 28, 30, 32, and may contact a pair of tracks that are connected to outer ring 14. As another example, roller bearings can be used in place of bearing balls 18, 20, 24, 26, 28, 30, 32.

Claims: 1. A bearing comprising: an outer ring (14) having an axis (12); an inner ring (16) for rotation relative to the outer ring about the axis (12); a plurality of bearing elements (18 to 32) radially disposed between the outer ring (14) and the inner ring (16); characterized by a) a plurality of rollers (34 to 48) peripherally disposed between the bearing elements (18 to 32) and radially disposed between the outer ring (12) and the inner ring (16); and b) at least one track (52, 56) for supporting the plurality of rollers. 2. The bearing of claim 1, characterized by: a pair of axially spaced tracks (52, 56) for supporting the plurality of rollers (34 to 48), said pair of tracks including a first track (52) fixedly connected to the inner ring (16) and a second track (56) fixedly connected to the inner ring. 3. The bearing of claim 2, characterized by: said pair of tracks (52, 56) have respective side plates (50, 54) disposed axially outwardly and on opposite sides of said bearing elements (18 to 32), said plates being fixedly connected to said inner ring (16), and said tracks (52, 56) having respective bearing surfaces (68, 70). 4. The bearing of one of the preceeding claims, characterized in that said bearing elements (18 to 32) are bearing balls. 5. The bearing of claim 3 or 4, characterized in that a) each said roller (34 to 48) has a left cylindrical portion (58) and a right cylindrical portion (60) and a recessed center portion (62); b) said left cylindrical portion (58) being arranged to bear against the first track bearing surface (68); c) said right cylindrical portion (60) being arranged to bear against the second track bearing surface (70); and d) said recessed center portion (62) being arranged to bear against an adjacent pair (18, 20) of the bearing balls (18 to 32) disposed at opposite sides thereof. 6. The bearing of claim 5, characterized in that said center portion (62) has a ring-shaped recess having an arcuate section with a radius (64) which is slightly larger than the radius (66) of the bearing ball (26). 7. The bearing of claim 6, characterized in that the center portion radius (64) measures between 52 percent to 55 percent of the diameter of the bearing ball. 8. The bearing of claim 5, 6 or 7, character­ ized in that the roller center portion (62) has a radius RR located at a point of contact between the roller (36) and the bearing ball (20) and disposed in a plane extending through spherical centers of the bearing balls, and wherein the radius is defined by the following formula: where: RI = radius of inner race RB = radius of the bearing ball ϑ = angle between bearing radii that intersect ball and roller centers, where N = number of bearing balls β = the complement of the angle between the line connecting the centers of the ball and roller, and the line connecting the centers of the ball and inner ring. 9. The bearing of claim 5, 6, 7 or 8, character­ ized in that the roller cylindrical portion (58, 60) at each end of the roller has a radius RA at the point of contact between the roller (36) and the roller track (52), and wherein said radius is defined by the following formula: where: RT = radius of the roller track RI = radius of the inner race RB = radius of the bearing ball ϑ = angle between bearing radii that intersect ball and roller centers, where N = number of bearing balls β = the complement of the angle between the line connecting the centers of the ball and roller, and the line connecting the centers of the ball and inner ring.

Inventors: JACOBSON, PETER E., SMITH, DENNIS W.
Applicants: HONEYWELL INC.
Application year: 1988
Main classification: F16C19
IPC codes: F16C19, F16C33