JP2012112506A - Spacer for bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a lightweight and low-cost spacer for a bearing which can reduce a torque loss during bearing rotation by reducing a sliding resistance with a counter member.SOLUTION: The spacer 4 for the bearing includes a pair of flange parts 14, 16 oppositely arranged making a ring shape, a plurality of column parts 18 which continuously extend over these flange parts and are arranged at predetermined intervals along the circumferential direction, and a plurality of opening pockets 20 constituted at predetermined intervals along the circumferential direction in the part surrounded by the pair of flange parts and the plurality of column parts. In the state incorporated between the bearings, the spacer 4 for the bearing relatively slides with its outer surface touching the bearing constitution being the counter member. By recessing the outer surfaces of both or one of flange parts and column parts in a predetermined range, the area of the outer surface of the spacer touching the bearing constitution as the counter member is made smaller, and the sliding resistance with the counter member is reduced.

Description

  The present invention relates to a technique for realizing a lightweight and low-cost bearing spacer that makes it possible to reduce torque loss during rotation of a bearing by reducing sliding resistance with a counterpart member.

  2. Description of the Related Art Conventionally, various types of radial roller bearings that rotate while supporting a radial load have been applied to parts where members rotate relative to each other, for example, an automatic transmission (AT) of an automobile and various reduction mechanisms (see Patent Document 1). ). As an example, FIG. 12A shows a planetary gear rotation support device in which a bearing spacer 4 is incorporated between a pair of radial roller bearings 2.

  The planetary gear rotation support device is a device for rotatably supporting the planetary gear 6 that revolves around the sun gear (not shown) while rotating in mesh with the sun gear. The planetary gear 6 has a hollow cylindrical shape, and is concentrically arranged along the outer periphery of the support shaft 8 formed in a columnar shape. Between the planetary gear 6 and the support shaft 8, a plurality of rolling elements (rollers) 10 are incorporated along the circumferential direction on both sides in the axial direction (the direction along the rotational axis Ax of the planetary gear 6). Both rolling elements (rollers) 10 are rotatably held by a cage 12.

  In this case, between the planetary gear 6 and the support shaft 8, for example, when the planetary gear 6 is an outer ring and the support shaft 8 is an inner ring, a plurality of rolling elements (rollers) 10 held by a pair of cages 12 are outside. A pair of radial roller bearings 2 incorporated between the inner rings 6 and 8 is configured. The spacer 4 is disposed between the planetary gear 6 and the support shaft 8 between the pair of radial roller bearings 2 (specifically, between the pair of cages 12) (for example, the planetary gear 6). And a pair of cages 12) are assembled in contact (sliding contact) with each other.

  As shown in FIG. 12 (b), the spacer 4 has a pair of flange portions 14, 16 arranged in an annular shape and opposed to each other, and extends continuously between the flange portions 14, 16. And a plurality of pillar portions 18 arranged at predetermined intervals along the circumferential direction, and a portion surrounded by the pair of flange portions 14 and 16 and the plurality of pillar portions 18 is provided in the circumferential direction. A plurality of opening pockets 20 are formed at a predetermined interval (for example, at equal intervals).

  Such a spacer 4 slides relatively while the outer surface of the spacer 4 is in contact (sliding contact) with the bearing structure as a counterpart member during the rotation of the bearing. Specifically, the outer diameter surfaces 14f and 16f of the flange portions 14 and 16 and the outer diameter surface 18f of the column portions 18 are in contact (sliding contact) with a bearing configuration (for example, the planetary gear 6) as a counterpart member. The side peripheral surfaces 14t and 16t of the flange portions 14 and 16 on the opposite side to the column portions 18 are in contact with a bearing configuration (for example, a pair of cages 12) as a counterpart member. (Sliding contact) and sliding relatively.

JP 2008-101725 A

  By the way, in various bearings (for example, see FIG. 12A) including the bearing of Patent Document 1 described above, a plurality of spacers 4 incorporated between a pair of radial roller bearings 2 (a pair of cages 12) are provided. By configuring the opening pocket 20, the weight of the spacer 4 itself can be reduced, and the cost of the spacer 4 can be reduced by, for example, reducing the material required for the spacer 4 by the number of the opening pocket 20. it can.

  However, in the various bearings described above (for example, see FIG. 12A), it is known that torque loss occurs during bearing rotation. Here, the ratio of the factor causing torque loss is 60% for the rolling resistance between the cage 12 and the rolling elements (rollers) 10, 20% for the stirring resistance between the cage 12, the spacer 4 and the lubricant, and the cage. 12 and the mating member (for example, the spacer 4 and the outer inner rings 6, 8) are considered to have a sliding (friction) resistance of about 20%.

  Accordingly, there is a demand for the development of a lightweight and low-cost bearing spacer that can reduce torque loss during rotation of the bearing by reducing sliding resistance with the mating member. Specifically, by reducing the contact (sliding contact) area of the spacer 4 that contacts (sliding contact) with the mating member (for example, the planetary gear 6 and the pair of cages 12), the spacer 4 and the mating member It is desired to reduce the sliding resistance (also referred to as frictional resistance) between them, and to reduce the ratio of factors causing torque loss due to such resistance.

  The present invention has been made to meet such demands, and its purpose is to reduce the torque loss during rotation of the bearing by reducing the sliding resistance with the counterpart member, and to reduce the torque loss. The object is to provide a low cost bearing spacer.

In order to achieve such an object, the present invention provides a pair of flange portions arranged in an annular shape and facing each other, and continuously extending between these flange portions, and in the circumferential direction. A plurality of pillars arranged at predetermined intervals along a plurality of opening pockets configured at predetermined intervals along the circumferential direction in a portion surrounded by a pair of flange parts and a plurality of pillars; A spacer for a bearing that slides relatively in contact with a bearing structure as a counterpart member in a state where it is incorporated between bearings, and either or both of each flange part and each pillar part. By denting one outer surface within a predetermined range, the area of the outer surface of the spacer in contact with the bearing structure as the counterpart member is reduced, and the sliding resistance with the counterpart member is reduced.
In the present invention, the pillars are arranged in parallel with each other along the circumferential direction or in an inclined manner.
In the present invention, each column portion is partially or partially arranged along the circumferential direction so that the circumferential width along the circumferential direction is smaller than the opening width along the circumferential direction of each opening pocket. A concave portion formed by being generally recessed is formed.
In the present invention, each flange portion is formed with a recess formed by being continuously or intermittently recessed along its circumferential direction.
In the present invention, each column portion is configured such that the entire outer surface thereof is recessed from the outer surface of each flange portion.
In the present invention, the respective pillar portions are arranged between the pair of flange portions in the circumferential direction, and are connected to each other by a connecting member interposed between the adjacent pillar portions along the circumferential direction. .

  According to the present invention, it is possible to realize a lightweight and low-cost bearing spacer that makes it possible to reduce torque loss during rotation of the bearing by reducing sliding resistance with the counterpart member.

The perspective view which shows the structure (structure which made small the contact area of the pillar part with respect to the other party member) of the bearing spacer which concerns on 1st Embodiment of this invention. The perspective view which shows the structure (The structure which made small the contact area of the pillar part with respect to the other party member) of the bearing spacer which concerns on 2nd Embodiment of this invention. The perspective view which shows the structure (The structure which made small the contact area of the pillar part with respect to the other party member) of the bearing spacer which concerns on 3rd Embodiment of this invention. The perspective view which shows the structure (The structure which made small the contact area of the pillar part with respect to the other party member) of the bearing spacer which concerns on 4th Embodiment of this invention. The perspective view which shows the structure (The structure which made small the contact area of the flange part with respect to the other party member) of the bearing spacer which concerns on 5th Embodiment of this invention. The perspective view which shows the structure (The structure which made small the contact area of the flange part with respect to the other party member) of the bearing spacer which concerns on 6th Embodiment of this invention. The perspective view which shows the structure (The structure which made small the contact area of the flange part with respect to the other party member) of the bearing spacer which concerns on 7th Embodiment of this invention. The perspective view which shows the structure (structure which extended the opening pocket) of the spacer for bearings concerning 8th Embodiment of this invention. The perspective view which shows the structure (structure which connected the pillar parts with the connection member) of the spacer for bearings concerning 9th Embodiment of this invention. The perspective view which shows the structure (structure which inclined each pillar part) of the bearing spacer which concerns on 10th Embodiment of this invention. (a) is a perspective view which shows the structure (structure which made the pillar part non-contact with respect to the other member) of the bearing spacer which concerns on 11th Embodiment of this invention, (b) is the figure (a). Sectional drawing which expands and shows a part of the shown spacer for bearings. (a) is a sectional view showing a configuration example in which a conventional bearing spacer is incorporated between a pair of radial roller bearings (between a pair of cages), and (b) is a configuration of a conventional bearing spacer. FIG.

  Hereinafter, the bearing spacer according to the embodiment of the present invention will be described with reference to the drawings. In addition, as a use aspect of the spacer for bearings which concerns on each embodiment mentioned later, as shown, for example to Fig.12 (a), the said spacer 4 is between a pair of radial roller bearings 2 (specifically, a pair of pair A case is assumed in which the members are assembled in a state of being in contact (sliding contact) with each other member (for example, the planetary gear (outer ring) 6 and the pair of cages 12).

  In addition, since the bearing spacer of each embodiment to be described later is based on the conventional bearing spacer 4 shown in FIG. 12B and has been improved, this will be described in the following. Stay. In this case, for the same configuration as the above-described bearing spacer 4 (FIG. 12B), the same reference numerals as those used in the configuration are attached to the drawings used in the embodiments described later. Therefore, the description is omitted.

  In addition, as an example of the specifications of the bearing spacer 4 (FIG. 12B) serving as a reference for each embodiment described later, the size of the spacer has an inner diameter of 5 to 30 mm and a wall thickness of 0.3 to 3.0 mm. Suppose that the total width is 2 to 30 mm, the opening width 20 h along the circumferential direction of the opening pocket 20 is set to 1 mm or more, and the outer diameter surfaces 14 f and 16 f of the flange portions 14 and 16 are set to 14 w and 16 w of 1 mm or more. .

  In this case, examples of the material for forming the spacer 4 include unheat-treated products such as cold rolled steel plate (SPCC), ultra-low carbon steel (AISI-1010), chromium molybdenum steel (SCM415), or carburizing or carbonitriding. For example, polyacetal, polyamide resin (nylon 46, nylon 66), polyphenylene sulfide resin (PPS), or the like may be applied.

  Further, as the roughness of the outer surface of the spacer, the outer diameter surfaces 14f and 16f and the side peripheral surfaces 14t and 16t of the flange portions 14 and 16, and the outer diameter surface 18f of the column portions 18 are each 6. Set to 3 Ra or less. In addition, Ra is prescribed | regulated as a parameter showing centerline average roughness or arithmetic average roughness.

“First Embodiment”
As shown in FIG. 1, the bearing spacer 4 according to the first embodiment has an outer surface (that is, an outer diameter surface 18f) of a plurality of column portions 18 arranged in parallel to each other along a circumferential direction within a predetermined range. By being recessed, the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing structure (for example, the planetary gear (outer ring) 6) as the counterpart member is reduced.

  Specifically, each column portion 18 is provided with the column portion 18 so that the circumferential width 18 w along the circumferential direction is smaller than the opening width 20 w along the circumferential direction of each opening pocket 20. A recess 18p formed by being partially recessed along the circumferential direction is configured. In this case, the concave portion 18p is configured to have a single hollow shape that extends in the longitudinal direction along the column portion 18 at the central portion of each column portion 18 and is continuous.

  Here, the size of the recess 18p is not particularly limited because it is set in consideration of, for example, the size of the column 18 and the strength of the column 18 remaining after the recess 18p is formed. In addition, as the shape of the recess 18p, the recess 18p recessed in a trapezoidal shape is shown as an example in the drawing, but is not limited to this, and for example, an arbitrary shape such as an arc shape, an ellipse shape, a rectangular shape, etc. Can be applied. Moreover, although the recessed part 18p is each formed in the circumferential direction both sides of each pillar part 18 as an example in drawing, you may form the recessed part 18p only in either one side.

  According to such a configuration, the circumferential width 18w of the central portion of each column 18 is smaller than each column 18 of the conventional spacer 4 (FIG. 12B) due to the recesses 18p on both sides in the circumferential direction. On the other hand, the opening width 20w of each opening pocket 20 is larger than the opening width 20h of each opening pocket 20 of the conventional spacer 4 (FIG. 12B) by an amount corresponding to the depression of each column 18 by the recess 18p. growing.

  As described above, according to the present embodiment, since the concave portions 18p are formed in each column portion 18, the area of the outer diameter surface 18f of each column portion 18 can be reduced by that amount. In this case, in a state in which the spacer 4 is incorporated between the pair of radial roller bearings 2 (specifically, between the pair of cages 12) (FIG. 12A), a bearing configuration as a mating member (for example, The area of the outer diameter surface 18f of each column 18 that contacts the planetary gear (outer ring) 6) can be made smaller than that of the conventional spacer 4 (FIG. 12B). As a result, the sliding resistance between the outer diameter surface 18f of each column 18 and the mating member can be greatly reduced as compared with the conventional spacer 4 (FIG. 12B).

  As a result, the outer surface of the spacer 4 (the outer diameter surfaces 14f and 16f and the side peripheral surfaces 14t and 16t of the flange portions 14 and 16 and the column portions are reduced by an amount corresponding to a reduction in the area of the outer diameter surface 18f of each column portion 18. The area over the entire outer diameter surface 18f) of 18 can be further reduced as compared with the conventional spacer 4 (FIG. 12B). Thereby, the contact (sliding contact) area of the spacer 4 that contacts (sliding contact) with the mating member (for example, the planetary gear (outer ring) 6 and the pair of cages 12) can be reduced. For this reason, the sliding resistance (friction resistance) between the spacer 4 and the mating member can be greatly reduced as compared with the conventional spacer 4 (FIG. 12B). The ratio of factors that cause torque loss can be drastically reduced.

  Moreover, according to this embodiment, since the recessed part 18p was formed in each pillar part 18, the weight reduction of each said pillar part 18 can be achieved. Thereby, the weight of the spacer 4 can be significantly reduced as compared with the conventional spacer 4 (FIG. 12B) by the amount of weight reduction of each column portion 18. In this case, the material required for the entire spacer 4 can be reduced by the number of the concave portions 18p. As a result, the cost of the spacer 4 can be reduced.

  Further, according to this embodiment, the spacer 4 together with the pair of radial roller bearings 2 is urged outward by the centrifugal force generated during the operation of the planetary gear rotation support device (FIG. 12A). Even when a bending stress acts on the support shaft (inner ring) 8, the spacer 4 can maintain a constant distance between the planetary gear (outer ring) 6 and the support shaft (inner ring) 8. At this time, since the spacer 4 incorporated in the center where the bending of the support shaft (inner ring) 8 becomes the largest is provided with a plurality of opening pockets 20, this reduces the inertial force, and the support shaft ( The bending of the inner ring) 8 can be effectively suppressed.

  In this case, the spacer 4 itself does not have a function of supporting the rotation of the planetary gear (outer ring) 6 and is not inherently provided with a large radial force. Therefore, in order to reduce the weight, each of the pockets 20 and the recesses 18p described above are provided. Even if it forms, the function and lifetime of the planetary gear rotation support device incorporating the spacer 4 between the pair of radial roller bearings 2 will not be reduced.

“Second Embodiment”
As shown in FIG. 2, the bearing spacer 4 according to the second embodiment has an outer surface (that is, an outer diameter surface 18f) of a plurality of pillars 18 arranged in parallel to each other along a circumferential direction within a predetermined range. By being recessed, the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing structure (for example, the planetary gear (outer ring) 6) as the counterpart member is reduced.

  Specifically, each column portion 18 is provided with the column portion 18 so that the circumferential width 18 w along the circumferential direction is smaller than the opening width 20 w along the circumferential direction of each opening pocket 20. A recess 18p formed by being partially recessed along the circumferential direction is configured. In this case, the concave portion 18p is configured to have a shape in which both side portions in the longitudinal direction of each column portion 18 are partially depressed along the column portion 18.

  As described above, according to the present embodiment, the circumferential width 18w of each side portion in the longitudinal direction of each column portion 18 is equal to each column portion 18 of the conventional spacer 4 (FIG. 12B) due to the recess portions 18p on both sides in the circumferential direction. Thus, the same effect as that of the first embodiment described above can be realized. Other configurations and the effects are the same as those in the first embodiment described above, and thus the description thereof is omitted.

“Third Embodiment”
As shown in FIG. 3, the bearing spacer 4 according to the third embodiment has an outer surface (that is, an outer diameter surface 18f) of a plurality of pillars 18 arranged in parallel to each other along a circumferential direction within a predetermined range. By being recessed, the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing structure (for example, the planetary gear (outer ring) 6) as the counterpart member is reduced.

  Specifically, each column portion 18 is provided with the column portion 18 so that the circumferential width 18 w along the circumferential direction is smaller than the opening width 20 w along the circumferential direction of each opening pocket 20. A recess 18p formed by being partially recessed along the circumferential direction is configured. In this case, the concave portion 18p is configured to have a shape in which the central portion of each column portion 18 and both side portions in the longitudinal direction are partially recessed along the column portion 18.

  As described above, according to the present embodiment, the circumferential width 18w of the three portions of the central portion and the both side portions in the longitudinal direction of each pillar portion 18 is determined by the conventional spacer 4 (FIG. 12B) by the recess portions 18p on both sides in the circumferential direction. ), The same effects as those of the first embodiment described above can be realized. Other configurations and the effects are the same as those in the first embodiment described above, and thus the description thereof is omitted.

“Fourth Embodiment”
As shown in FIG. 4, the bearing spacer 4 according to the fourth embodiment has an outer surface (that is, an outer diameter surface 18 f) of a plurality of pillars 18 arranged in parallel to each other along a circumferential direction within a predetermined range. By being recessed, the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing structure (for example, the planetary gear (outer ring) 6) as the counterpart member is reduced.

  Specifically, each column portion 18 is provided with the column portion 18 so that the circumferential width 18 w along the circumferential direction is smaller than the opening width 20 w along the circumferential direction of each opening pocket 20. A recess 18p formed by being partially recessed along the circumferential direction is configured. In this case, the concave portion 18 p is configured to have a shape in which both side portions in the longitudinal direction near the central portion of each column portion 18 are partially recessed along the column portion 18.

  As described above, according to the present embodiment, the two circumferential widths 18w of the two longitudinal side portions near the central portion of each columnar portion 18 have the conventional spacers 4 (FIG. 12B) by the concave portions 18p on both circumferential sides. )), Which is smaller than each column portion 18, thereby achieving the same effects as those of the first embodiment described above. Other configurations and the effects are the same as those in the first embodiment described above, and thus the description thereof is omitted.

“Fifth Embodiment”
As shown in FIG. 5, the bearing spacer 4 according to the fifth embodiment has the outer surfaces (that is, the outer diameter surfaces 14 f and 16 f and the side peripheral surfaces 14 t and 16 t) of the pair of flange portions 14 and 16 within a predetermined range. By recessing, it is configured to reduce the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing configuration (for example, the planetary gear (outer ring) 6 and the pair of cages 12) as a counterpart member. .

  Specifically, the flange portions 14 and 16 are respectively provided with concave portions 14p and 16p formed by being continuously depressed along the circumferential direction thereof. In this case, the recesses 14p, 16p are configured as conical tapered surfaces that are tapered in a tapered manner as they go from the outer diameter surfaces 14f, 16f to the side peripheral surfaces 14t, 16t and continue along the circumferential direction.

  Here, the sizes (widths) of the recesses 14p, 16p are set according to the sizes of the flange portions 14, 16 (widths of the outer diameter surfaces 14f, 16f and the side peripheral surfaces 14t, 16t), for example. Therefore, there is no particular limitation here. Further, the inclination angles of the recesses 14p, 16p can be arbitrarily set within a range of more than 90 ° without including 0 °. Other configurations are the same as those of the spacer 4 shown in FIG.

  As described above, according to the present embodiment, since the concave portions 14p and 16p are formed in the flange portions 14 and 16, the outer surfaces of the flange portions 14 and 16 (that is, the outer diameter surfaces 14f and 16f, The area of the side peripheral surfaces 14t and 16t can be made smaller than the flange portions 14 and 16 of the conventional spacer 4 (FIG. 12B).

  In this case, in a state in which the spacer 4 is incorporated between the pair of radial roller bearings 2 (specifically, between the pair of cages 12) (FIG. 12A), a bearing configuration as a mating member (for example, The area of the outer diameter surfaces 14f and 16f of the flange portions 14 and 16 in contact with the planetary gear (outer ring) 6) can be further reduced as compared with the conventional spacer 4 (FIG. 12B), Compared to the conventional spacer 4 (FIG. 12B), the area of the side peripheral surfaces 14t and 16t of the flange portions 14 and 16 contacting the bearing structure (for example, a pair of cages 12) as the counterpart member is larger. It can be further reduced. As a result, the sliding resistance between the outer diameter surfaces 14f and 16f and the side peripheral surfaces 14t and 16t of the flange portions 14 and 16 and the mating member is significantly larger than that of the conventional spacer 4 (FIG. 12B). Can be reduced.

  As a result, the outer surface of the spacer 4 (the outer diameter surfaces 14f and 16f of the flange portions 14 and 16 is reduced by the area of the outer diameter surfaces 14f and 16f and the side peripheral surfaces 14t and 16t of the flange portions 14 and 16, respectively. In addition, the entire area of the side peripheral surfaces 14t and 16t and the outer diameter surface 18f of each column 18 can be further reduced as compared with the conventional spacer 4 (FIG. 12B). Thereby, the contact (sliding contact) area of the spacer 4 that contacts (sliding contact) with the mating member (for example, the planetary gear (outer ring) 6 and the pair of cages 12) can be reduced. For this reason, the sliding resistance (friction resistance) between the spacer 4 and the mating member can be greatly reduced as compared with the conventional spacer 4 (FIG. 12B). The ratio of factors that cause torque loss can be drastically reduced.

  Moreover, according to this embodiment, since the recessed parts 14p and 16p were formed in each flange part 14 and 16, the weight reduction of each said flange part 14 and 16 can be achieved. Thereby, the weight of the spacer 4 can be significantly reduced compared with the conventional spacer 4 (FIG. 12B) by the amount of weight reduction of the flange portions 14 and 16. In this case, the material required for the entire spacer 4 can be reduced by the number of the concave portions 14p, 16p, and as a result, the cost of the spacer 4 can be reduced.

  Since other effects are the same as those in the first embodiment, the description thereof is omitted. In this case, the configuration of the present embodiment (that is, the configuration in which the concave portions 14p and 16p are formed in the flange portions 14 and 16) may be applied to the first to fourth embodiments described above. Thereby, the spacer 4 which has the effect which concerns on the said 1st-4th embodiment, and the effect which concerns on this embodiment is realizable.

“Sixth Embodiment”
As shown in FIG. 6, the bearing spacer 4 according to the sixth embodiment has the outer surfaces of the pair of flange portions 14 and 16 (that is, the outer diameter surfaces 14 f and 16 f and the side peripheral surfaces 14 t and 16 t) within a predetermined range. By recessing, it is configured to reduce the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing configuration (for example, the planetary gear (outer ring) 6 and the pair of cages 12) as a counterpart member. .

  Specifically, the flange portions 14 and 16 are respectively provided with recess portions 14s and 16s formed by being intermittently recessed along the circumferential direction. In this case, the recesses 14s and 16s have a rectangular shape that is recessed from the side peripheral surfaces 14t and 16t so as to partially enter the outer diameter surfaces 14f and 16f, and are arranged at predetermined intervals along the circumferential direction. Configured.

  Here, the sizes of the recesses 14s and 16s are set in consideration of, for example, the size of the flanges 14 and 16 and the strength of the flanges 14 and 16 remaining after forming the recesses 14s and 16s. Then there is no particular limitation. Further, as the shapes of the recesses 14s and 16s, the recesses 14s and 16s recessed in a rectangular shape are shown as an example in the drawing, but the invention is not limited to this, and for example, an arc shape, an elliptical shape, a triangular shape, and the like Any shape can be applied. In the drawings, as an example, the recesses 14 s and 16 s are formed so as to align with both side positions of each column part 18, but both side positions of each opening pocket 20 or both the column part 18 and the opening pocket 20. The recesses 14s and 16s may be formed so as to align with the overlapping positions on both sides.

  Moreover, in this embodiment, it replaces with the recessed parts 14p and 16p of above-described 5th Embodiment, and the recessed parts 14s and 16s are comprised, The other structure is the same as that of the spacer 4 which concerns on above-mentioned 5th Embodiment. Therefore, the description thereof is omitted. Further, the effects of this embodiment are the same as those of the fifth embodiment described above, and thus the description thereof is omitted. In this case, the configuration of the present embodiment (that is, the configuration in which the concave portions 14s and 16s are formed in the flange portions 14 and 16) may be applied to the first to fourth embodiments described above. Thereby, the spacer 4 which has the effect which concerns on the said 1st-4th embodiment, and the effect which concerns on this embodiment is realizable.

“Seventh Embodiment”
As shown in FIG. 7, the bearing spacer 4 according to the seventh embodiment has the outer surfaces of the pair of flange portions 14 and 16 (that is, the outer diameter surfaces 14f and 16f and the side peripheral surfaces 14t and 16t) within a predetermined range. By recessing, it is configured to reduce the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing configuration (for example, the planetary gear (outer ring) 6 and the pair of cages 12) as a counterpart member. .

  Specifically, the flange portions 14 and 16 are respectively provided with concave portions 14g and 16g formed by being intermittently recessed along the circumferential direction. In this case, the recesses 14g and 16g are formed by notching (removing and removing) the flange portions 14 and 16 alternately at predetermined intervals and alternately so that the side peripheral surfaces 14t and 16t and the outer diameter of the notch portions are formed. The surfaces 14f and 16f are configured to be recessed.

  Here, paying attention to the opening pockets 20 adjacent in the circumferential direction, in the flange portions 14 and 16 located on both sides of the one adjacent opening pocket 20, for example, a part of the flange portion 14 on one side is notched to open the opening pocket 20. When one concave portion 14g communicating with the pocket 20 is formed, the flange portions 14 and 16 located on both sides of the other adjacent opening pocket 20 have, for example, the opposite side which is in a different positional relationship with the concave portion 14g described above. A part of the flange portion 16 is cut out to form one concave portion 16 g communicating with the opening pocket 20. By repeating such a forming procedure, recesses 14g and 16g cut out alternately along the flange portions 14 and 16 are formed.

  As described above, in the present embodiment, the recesses 14g and 16g are configured instead of the recesses 14p and 16p of the above-described fifth embodiment, and other configurations are the same as those of the spacer 4 according to the above-described fifth embodiment. Therefore, the description thereof is omitted. Further, the effects of this embodiment are the same as those of the fifth embodiment described above, and thus the description thereof is omitted. In this case, the configuration of the present embodiment (that is, the configuration in which the concave portions 14g and 16g are formed in the flange portions 14 and 16) may be applied to the first to fourth embodiments described above. Thereby, the spacer 4 which has the effect which concerns on the said 1st-4th embodiment, and the effect which concerns on this embodiment is realizable.

“Eighth Embodiment”
As shown in FIG. 8, the bearing spacer 4 according to the eighth embodiment has an outer surface (that is, an outer diameter surface 18 f) of a plurality of pillars 18 arranged in parallel to each other along a circumferential direction within a predetermined range. By being recessed, the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing structure (for example, the planetary gear (outer ring) 6) as the counterpart member is reduced.

  Specifically, each column portion 18 is provided with the column portion 18 so that the circumferential width 18 w along the circumferential direction is smaller than the opening width 20 w along the circumferential direction of each opening pocket 20. A recess 18p is formed which is formed to be entirely recessed along the circumferential direction. In this case, as a method of forming the recess 18p, a method of recessing the entire length of each column 18 over the entire length in the longitudinal direction, thinning out each column 18 for every one or a plurality of others (for example, (Removal, deletion) can be applied.

  As described above, according to this embodiment, the area of the outer surface of the spacer 4 that comes into contact (sliding contact) with the bearing configuration (for example, the planetary gear (outer ring) 6) as the counterpart member is the same as that of the conventional spacer 4 (FIG. )), It is possible to achieve the same effect as in the first embodiment. The other configuration is the same as that of the spacer 4 shown in FIG.

“Ninth Embodiment”
As shown in FIG. 9, in the bearing spacer 4 according to the ninth embodiment, each column portion 18 is disposed across the circumferential direction between the pair of flange portions 14 and 16 and is adjacent along the circumferential direction. They are connected to each other by a connecting member 22 interposed between the matching column portions 18. Each connecting member 22 has a substantially arc shape, and in a state where the column portions 18 are connected to each other, the entire contour thereof is identical to or equivalent to each flange portion 14, 16. It is configured.

  Specifically, in the above-described eighth embodiment, the connecting member 22 is recessed throughout the entire length in the longitudinal direction of each column portion 18 to form a recess 18p (that is, each opening pocket 20). It is provided in order to improve the strength of the spacer 4 (the occupied area is expanded). In this case, the connecting member 22 may be arranged along the circumferential direction or may be inclined. In short, what is necessary is just to be comprised so that the intensity | strength of the spacer 4 can be improved by interposing the said connection member 22 between the pillar parts 18. FIG. Since other configurations and effects are the same as those of the spacer 4 according to the above-described eighth embodiment, description thereof is omitted.

“Tenth Embodiment”
As shown in FIG. 10, in the bearing spacer 4 according to the tenth embodiment, the column portions 18 are arranged in an inclined manner along the circumferential direction. Specifically, in the above-described eighth embodiment, in order to improve the strength of the spacer 4 that is recessed throughout the entire length in the longitudinal direction of each column 18 to form the recess 18p, each column 18 Are inclined to each other. Since the other configuration is the same as that of the spacer 4 according to the above-described eighth embodiment, the description thereof is omitted.

  As described above, according to the present embodiment, a so-called “truss structure” constructed based on triangles along the circumferential direction can be constructed by the flange portions 14 and 16 and the column portions 18 inclined with respect to each other. Therefore, the strength of the spacer 4 can be significantly improved. In this case, you may apply the truss structure of this embodiment (namely, the arrangement | positioning structure which mutually inclined each pillar part 18 along the circumferential direction) to the above-mentioned 1st-4th embodiment. Thereby, the spacer 4 which has the effect which concerns on the said 1st-4th embodiment, and the effect which concerns on this embodiment is realizable.

“Eleventh Embodiment”
As shown in FIGS. 11A and 11B, in the bearing spacer 4 according to the eleventh embodiment, each columnar portion 18 has the entire outer surface (that is, the outer diameter surface 18 f) of each flange portion 14. 16 are recessed from the outer surface (that is, the outer diameter surfaces 14f and 16f). In this case, the thickness of each column 18 is reduced, and the outer diameter surface 18f thereof is recessed from the outer diameter surfaces 14f, 16f of the flange portions 14, 16, so that the outer diameter surface 18f of each column 18 is Each of the first and second recesses is formed with a recess (in particular, no reference numeral is attached).

  As described above, according to the present embodiment, the concave portions are formed on the outer diameter surfaces 18f of the respective column portions 18, thereby making contact (sliding contact) with the bearing configuration (for example, the planetary gear (outer ring) 6) as the counterpart member. Since the area of the outer surface of the spacer 4 can be made smaller than that of the conventional spacer 4 (FIG. 12B), the same effect as in the first embodiment can be realized. The other configuration is the same as that of the spacer 4 shown in FIG.

4 Spacers 14, 16 Flange 18 Column 20 Opening pocket

Claims (6)

A pair of flange portions arranged opposite each other in an annular shape;
A plurality of pillar portions extending continuously between the flange portions and arranged at predetermined intervals along the circumferential direction;
Provided with a plurality of opening pockets configured at predetermined intervals along the circumferential direction in a portion surrounded by a pair of flange portions and a plurality of pillar portions,
A spacer for a bearing that slides relatively in contact with the bearing structure as a counterpart member in a state where the bearings are assembled between the bearings,
By reducing the outer surface of each flange part and each pillar part, or any one of the outer surfaces within a predetermined range, the area of the outer surface of the spacer in contact with the bearing structure as the counterpart member is reduced. The bearing spacer according to claim 1, wherein the sliding resistance of the bearing is reduced.   The bearing spacer according to claim 1, wherein the pillar portions are arranged in parallel with each other along the circumferential direction or in an inclined manner.   Each pillar is partially or entirely recessed along the circumferential direction so that the circumferential width along the circumferential direction is smaller than the opening width along the circumferential direction of each opening pocket. The bearing spacer according to claim 2, wherein a concave portion formed by bending is formed.   The bearing spacer according to any one of claims 1 to 3, wherein each flange portion includes a recess formed by being continuously or intermittently recessed along a circumferential direction thereof.   The bearing spacer according to claim 1, wherein each column portion is configured such that an entire outer surface thereof is recessed from an outer surface of each flange portion.   Each column part is arranged over a peripheral direction between a pair of flange parts, and is mutually connected by a connecting member interposed between adjacent column parts along the circumferential direction. The spacer for a bearing according to claim 3.

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