JP2006132705A - Rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To promote the revolution of a retainer and a rolling element, and to prevent the partial wear (wear at clearance of rolling elements) of the track surface of a bearing ring, when the bearing ring of the rolling bearing is reciprocated, for example, accompanied by the reciprocation at a fixed angle, of a shaft supported by a rolling bearing. <P>SOLUTION: A retainer 13 is guided by allowing its outside-diameter face 13a as a guide face at the retainer side to be slid and kept into contact with the inside-diameter face 11a of an outer ring 11 as a guide face at a bearing ring side, and the outside-diameter face 14 is formed with a sawtooth projecting and recessed portion 20. The projecting and recessed portion 20 generates a difference in frictional force between a flange inside-diameter face 11a that is the guide face at the bearing ring side at the reciprocation, going and return of the outer ring 11, and the retainer 13, and thus a rotating (revolving) force in one direction is generated at the retainer 13. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a rolling bearing in which a plurality of rolling elements held by a cage are supported between a pair of races so as to be freely rotatable, and more specifically, for example, even when a supporting shaft reciprocates at a constant angle. The present invention relates to a structure of a rolling bearing for ensuring durability.

Conventionally, various types of roller bearings have been proposed (see, for example, Patent Documents 1 and 2).
FIG. 8 is a cross-sectional view of the main part showing the cylindrical roller bearing disclosed in Patent Document 1, and FIG. 9 is a perspective view showing the cylindrical roller of the cylindrical roller bearing of FIG.

  As shown in FIGS. 8 and 9, the cylindrical roller bearing 100 includes an inner ring 101 having an inner ring raceway 101a on an outer peripheral surface, an outer ring 102 having an outer ring raceway 102a on an inner peripheral face, and an inner ring raceway 101a and an outer ring raceway 102a. A plurality of cylindrical rollers 103 provided so as to be capable of rolling, and a cage 104 provided rotatably between the inner ring raceway 101a and the outer ring raceway 102a while holding each cylindrical roller 103.

  A pair of flanges 102b are provided at both ends of the outer ring raceway 102a, and each flange 102b prevents the cylindrical rollers 103 from being displaced in the axial direction by sandwiching the cylindrical rollers 103 from both sides in the axial direction. Further, a chamfered portion 103c is provided between the rolling surface 103a of the cylindrical roller 103 and both axial end surfaces 103b. The radius of curvature of the chamfered portion 103c that connects the rolling surface 103a and the chamfered portion 103b is 0.3 mm or more.

  FIG. 10 is a cross-sectional view of the main part showing the roller bearing disclosed in Patent Document 2, and FIG. 11 is a main part showing the end of the cylindrical roller that is in sliding contact with the collar part of the roller bearing of FIG. FIG.

As shown in FIGS. 10 and 11, the roller bearing 110 includes an outer ring 111, an inner ring 112, a cylindrical roller 113, and a cage 114, and a flange 112 a is provided at the right end portion of the inner ring 112 in the drawing. . The flange 112a guides the cylindrical roller 110 in the circumferential direction of the outer ring 111 and the inner ring 112, and has a roller guide surface 112c that is substantially perpendicular to the raceway surface 112b of the inner ring 112. The cylindrical roller 110 is slidably contacted with the roller guide surface 112c of the flange portion 112a at the end surface 110a, and is rolled on the raceway surface 112b of the inner ring 112.
Flange portion 112a and the sliding contact end surface 110a of the cylindrical roller 110, the outer shape line 110b of the cross-section through a first point _{P A,} and successive passes between the third point _{P C} and the fourth point _{P D} It is ground with an elastic grindstone into a curved shape.
Japanese Patent Laid-Open No. 7-12133 (pages 2 and 3, FIGS. 1 and 5) Japanese Unexamined Patent Publication No. 2003-2145 (pages 3 to 4, FIGS. 1 and 2)

  In the cylindrical roller bearing 100 (FIGS. 8 and 9) and the roller bearing 110 (FIGS. 10 and 11) which are the conventional rolling bearings described above, in any case, the flange between the cylindrical rollers 103 and 110 and the outer ring 102 or the inner ring 112 Friction heat generated between the portions 102b and 112a can be reduced, and wear and seizure of the portions can be prevented.

  However, for example, when the supporting shaft reciprocates at a constant angle, the revolution of the cage and the rolling element becomes insufficient, and the cage and the rolling element often stop at the same position on the raceway surface of the raceway. . Therefore, there has been a problem that uneven wear may occur and progress on the raceway surface of the raceway at intervals of the rolling elements, and malfunction may occur at an early stage.

  The present invention has been made in view of the above circumstances, and even when a shaft supported by a rolling bearing reciprocates at a certain angle, for example, even when a bearing ring of the rolling bearing reciprocates, An object of the present invention is to provide a rolling bearing capable of promoting the revolution of a moving body and thereby preventing uneven wear of the raceway surface of the raceway ring (abrasion at the rolling element spacing).

  1) A rolling bearing according to the present invention is a rolling bearing in which a plurality of rolling elements held by a cage are supported between a pair of race rings so as to be freely rollable. The cage is a guide surface on the race ring side. And a guide surface on the cage side, and at least one of the guide surface on the raceway side or the guide surface on the cage side is formed with a sawtooth-shaped uneven portion. It is characterized by that.

According to the rolling bearing having the above-described configuration, when the shaft to be supported reciprocates at a constant angle, for example, when the raceway reciprocates, the guide surface on the raceway side is maintained during the forward and backward movement of the raceway. The frictional force between the cage causes a difference due to the serrated irregularities, which generates a rotational (revolution) force in one direction in the cage, facilitating the revolution of the cage and rolling elements. Is done. As a result, uneven wear (abrasion at rolling element intervals) on the raceway surface of the raceway is prevented, and a rolling bearing with excellent durability can be obtained.
In addition, if serrated irregularities are formed on both the guide surface on the raceway side and the guide surface on the cage side, the cage is given a larger rotational (revolution) force in one direction. Revolution of the vessel and rolling element is further strongly promoted.

  2) The rolling bearing of the present invention is the rolling bearing according to 1), wherein the serrated irregularities are convex portions of a circumferential surface that is a part of the guide surface on the raceway side or the guide surface on the cage side. A gradual slope that forms a gentle angle with respect to the tangential direction of the circumferential surface, and a steep slope that forms a steep angle with respect to the tangential direction of the circumferential surface. And the number of circumferential surfaces is three or more at equal intervals along the guide surface on the raceway side or the annular direction on the cage side. .

  According to the rolling bearing having the above-described configuration, when the shaft to be supported reciprocates at a constant angle, for example, when the raceway reciprocates, the guide surface on the raceway side is maintained during the forward and backward movement of the raceway. There is a difference in the frictional force between the two parts due to the serrated irregularities formed by continuously forming gentle and steep slopes on both sides in the annular direction of each circumferential surface. Since there are three or more circumferentially spaced intervals, a rotating (revolving) force in one direction of the cage is almost always generated in at least one of the convex portions while maintaining the weight balance of the cage, and the cage and rolling element Revolution is promoted. Thereby, uneven wear (abrasion at the rolling element interval) on the raceway surface of the raceway is prevented, and a rolling bearing with excellent durability can be obtained.

  3) The rolling bearing of the present invention is the rolling bearing described in 2) above, wherein the total ring-direction length of each circumferential surface of the serrated irregularities is a guide surface on the bearing ring side or a guide on the cage side. It is characterized by being 20% or more of the annular length of the surface.

  According to the rolling bearing having the above-described configuration, the total annular direction length of each circumferential surface of the concavo-convex portion is 20% or more of the annular direction length of the guide surface on the bearing ring side or the guide surface on the cage side. Accordingly, the function of each circumferential surface as the guide surface on the raceway side or the guide surface on the cage side is ensured, and a rolling bearing with excellent rotational characteristics is obtained.

  According to the rolling bearing of the present invention, it is possible to prevent uneven wear (wear at the rolling element interval) on the raceway surface of the bearing ring, and to ensure high durability.

  Hereinafter, the present invention will be described with reference to illustrated embodiments.

  FIG. 1 is a cross-sectional view showing a cylindrical roller bearing with an outer ring collar, which is a rolling bearing according to a first embodiment of the present invention, and FIG. 2 is a schematic enlarged view of part A of FIG.

  Referring to FIGS. 1 to 2, the cylindrical roller bearing 10 with the outer ring collar of the first embodiment includes a plurality of cage rings 13 held between a outer ring 11 and an inner ring 12 that are a pair of race rings. The cylindrical roller 14 is configured to freely roll, and the cage 13 is guided by the flange inner diameter surface 11 a of the outer ring 11.

  The cage 13 is guided by sliding the outer diameter surface 13a, which is a guide surface on the cage side, to the collar inner surface 11a of the outer ring 11, which is the guide surface on the raceway side, and the outer diameter surface. 13a is formed with a sawtooth-shaped concavo-convex portion 20. The concave-convex portion 20 causes a difference in the frictional force between the collar inner surface 11a, which is the guide surface on the raceway ring side, and the cage 13 when the outer ring 11 is reciprocated, forward-moved, and backward-moved. A rotational (revolution) force in one direction is generated in 13.

  That is, the concavo-convex portion 20 has the circumferential surface 21 which is a part of the outer diameter surface 13a of the cage 13 as the apex of the convex portion 22, and is on both sides in the annular direction of the circumferential surface 21 (in FIG. 1, both left and right sides). Continuously, a gentle slope 23 that forms a gentle angle α1 (FIG. 2) of, for example, 1 to 10 ° with respect to the tangential B direction (FIGS. 1 and 2) of the outer diameter surface 13a of the cage 13, and the outer diameter surface 13a And a steep slope 24 having a steep angle α2 (FIG. 2) of, for example, 20 to 90 ° with respect to the tangential line B, and is configured to be uneven. The number of the convex portions 22 is a plurality (for example, 3 or more) at regular intervals along the annular direction of the cage 13.

  In the concavo-convex portion 20, a concave portion 25 is constituted by a gentle slope 23 and a steep slope 24 that are continuous on both sides in the annular direction of each convex portion 22 (left and right sides in FIG. 1), and each concave portion 25 corresponds to each convex portion 22. Thus, the shape is asymmetric in FIG. The total length L in the annular direction of each circumferential surface 21 is 20% or more of the length in the annular direction of the outer diameter surface 13a of the cage 13, and each circle as a guide surface of the cage 13 is used. The function of the peripheral surface 21 is ensured.

  In such a cylindrical roller bearing 10, when a supported shaft (not shown) reciprocates at a constant angle, for example, when the outer ring 11 of the cylindrical roller bearing 10 reciprocates, the outer ring 11 moves forward and backward. In the frictional force between the flange inner diameter surface 11a of the outer ring 11 and the cage 13, a difference is caused due to the serrated uneven portion 20. Then, due to the difference in frictional force, a rotational (revolution) force in one direction is generated in the cage 13. Thereby, the revolution of the cage 13 and the cylindrical roller 14 is promoted, and uneven wear (wear at the interval between the cylindrical rollers) on the raceways of the outer ring 11 and the inner ring 12 is prevented.

  FIG. 3 is a sectional view showing a cylindrical roller bearing with an outer ring collar which is a rolling bearing according to a second embodiment of the present invention.

Referring to FIG. 3, in the cylindrical roller bearing 30 with the outer ring collar of the second embodiment, the serrated uneven portion 20 is formed not on the outer diameter surface 31 a of the cage 31 but on the collar inner diameter surface 32 a of the outer ring 32. ing.
Other configurations and operations are the same as those in the first embodiment.

  FIG. 4 is a sectional view showing a cylindrical roller bearing with an inner ring collar which is a rolling bearing according to a third embodiment of the present invention.

Referring to FIG. 4, in the cylindrical roller bearing 40 with the inner ring collar of the third embodiment, the cage 41 is guided by the collar outer diameter surface 42 a of the inner ring 42. That is, the cage 41 is guided by sliding the inner diameter surface 41a, which is a guide surface on the cage side, into sliding contact with the collar outer diameter surface 42a of the inner ring 42, and a serrated uneven portion on the inner diameter surface 41a. 20 is formed.
Other configurations and operations are the same as those in the first embodiment.

  FIG. 5 is a sectional view showing a cylindrical roller bearing with an inner ring collar which is a rolling bearing according to a fourth embodiment of the present invention.

Referring to FIG. 5, in the cylindrical roller bearing 50 with the inner ring collar of the fourth embodiment, the serrated irregularities 20 are formed not on the inner diameter surface 51 a of the cage 51 but on the outer diameter surface 52 a of the inner ring 52. ing.
Other configurations and operations are the same as those in the third embodiment.

  FIG. 6 is a sectional view showing a cylindrical roller bearing with an outer ring collar which is a rolling bearing according to a fifth embodiment of the present invention.

Referring to FIG. 6, in the cylindrical roller bearing 60 with the outer ring collar of the fifth embodiment, the serrated irregularities 20 are formed on both the outer diameter surface 61 a of the retainer 61 and the collar inner diameter surface 62 a of the outer ring 62. Has been.
Other configurations and operations are the same as those in the first embodiment.

  FIG. 7: is sectional drawing which shows the cylindrical roller bearing with an inner ring collar which is a rolling bearing of 6th Embodiment of this invention.

Referring to FIG. 7, in the cylindrical roller bearing 70 with the inner ring collar of the sixth embodiment, the serrated irregularities 20 are formed on both the inner diameter surface 71 a of the retainer 71 and the outer diameter surface 72 a of the inner ring 72. Has been.
Other configurations and operations are the same as those in the third embodiment.

  As described above, according to each of the embodiments described above, in the cylindrical roller bearings 10, 30, 60 with the outer ring collar, a saw-tooth shape for generating a rotating (revolving) force in one direction on the cages 13, 31, 61. The concavo-convex portion 20 is the outer diameter surface 13a (first embodiment) of the cage 13, the collar inner diameter surface 32a (second embodiment) of the outer ring 32, or the outer diameter surface 61a of the cage 61 and the collar inner diameter of the outer ring 62. It is formed on both surfaces 62a (fifth embodiment). Further, in the cylindrical roller bearings 40, 50, 70 with the inner ring collar, the serrated irregularities 20 for generating a rotational (revolving) force in one direction on the cages 41, 51, 71 are provided on the cage 41. Both the inner diameter surface 41a (third embodiment), the collar outer diameter surface 52a (fourth embodiment) of the inner ring 52, or both the inner diameter surface 71a of the retainer 71 and the collar outer diameter surface 72a of the inner ring 72 (sixth embodiment). Is formed.

  Therefore, when the shaft ring supported by the cylindrical roller bearing reciprocates at a fixed angle, for example, when the raceway of the cylindrical roller bearing reciprocates, the raceway side of the raceway side during forward and backward movement of the raceway ring is reduced. A difference can be produced in the frictional force between the guide surface and the cage. Due to the difference in the frictional force, the cage can generate a rotational (revolution) force in one direction, and the revolution of the cage and the rolling element can be promoted. As a result, uneven wear (wear at intervals between the cylindrical rollers) on the raceway surface of the raceway can be prevented, and high durability can be ensured.

  Further, according to the fifth and sixth embodiments, the serrated uneven portion 20 for generating a rotational (revolution) force in one direction on the cage is formed by the outer diameter surface 61 a and the outer ring 62 of the cage 61. Since it is formed on both the inner diameter surface 62a of the collar (fifth embodiment) or both the inner diameter surface 71a of the cage 71 and the collar outer diameter surface 72a of the inner ring 72 (sixth embodiment), the cages 61 and 71 are formed. Rotational (revolution) force generated in one direction can be further increased, and the revolution of the cages 61 and 71 and the cylindrical roller 14 can be further strongly promoted.

  In addition, the serrated uneven portion 20 is a guide surface of the bearing ring (in the case where the guide surface is an inner ring, in the case of a roller bearing, the collar outer diameter portion, in the case of a ball bearing, the inner ring outer diameter portion, and in the case where the guide surface is an outer ring, When the roller bearing is formed at the inner diameter of the collar and the inner diameter of the outer ring at the ball bearing (in the above embodiment, the second, fourth, fifth and sixth embodiments), the interference between the concavo-convex portion and the rolling element In order to prevent this, the depth of the recess and the chamfering and sag of the guide surface are adjusted so that the depth of the recess does not exceed the chamfering and sag of the guide surface.

  The rolling bearing obtained by the present invention is preferably used in a swinging motion part in which a supported shaft reciprocates at a constant angle, for example, and prevents high wear and tear on the raceway surface due to the reciprocating motion of the raceway ring. Sex is secured.

It is sectional drawing which shows the cylindrical roller bearing with the outer ring collar which is a rolling bearing of 1st Embodiment of this invention. FIG. 2 is a schematic enlarged side view of a part A in FIG. 1. It is sectional drawing which shows the cylindrical roller bearing with the outer ring collar which is a rolling bearing of 2nd Embodiment of this invention. It is sectional drawing which shows the cylindrical roller bearing with an inner ring collar which is a rolling bearing of 3rd Embodiment of this invention. It is sectional drawing which shows the cylindrical roller bearing with an inner ring collar which is a rolling bearing of 4th Embodiment of this invention. It is sectional drawing which shows the cylindrical roller bearing with the outer ring collar which is a rolling bearing of 5th Embodiment of this invention. It is sectional drawing which shows the cylindrical roller bearing with an inner ring collar which is a rolling bearing of 6th Embodiment of this invention. It is principal part sectional drawing which shows the cylindrical roller bearing currently disclosed by patent document 1. FIG. It is a perspective view which shows the cylindrical roller of the cylindrical roller bearing of FIG. FIG. 6 is a cross-sectional view of a main part showing a roller bearing disclosed in Patent Document 2. It is principal part sectional drawing which shows the edge part of the cylindrical roller of the part which slidably contacts with the collar part of the roller bearing of FIG.

Explanation of symbols

10 Cylindrical roller bearings 11 Race rings (outer rings)
11a Raceway side guide surface (outer ring collar inner surface)
12 Race ring (inner ring)
13 Cage 13a Cage guide surface (outer diameter surface of cage)
14 Rolling elements (cylindrical rollers)
20 Serrated Uneven part 21 Circumferential surface 22 Convex part 23 Slow slope 24 Steep slope 25 Concave part B Tangent of outer diameter surface of cage

Claims (3)

In a rolling bearing formed by supporting a plurality of rolling elements held by a cage in a freely rollable manner between a pair of race rings,
The cage is guided by sliding contact between the guide surface on the raceway side and the guide surface on the cage side, and at least one of the guide surface on the raceway side or the guide surface on the cage side Is a rolling bearing characterized in that serrated irregularities are formed. The serrated irregularities are circular on the circumferential surface, which is a part of the guide surface on the raceway side or the guide surface on the cage side, with the apex of the convex part continuously on both sides in the annular direction of the circumferential surface. It is formed in a concavo-convex shape by forming a gentle slope that makes a gentle angle with respect to the tangential direction of the circumferential surface and a steep slope that makes a sharp angle with respect to the tangential direction of the circumferential surface,
The rolling bearing according to claim 1, wherein the number of the convex portions is three or more at regular intervals along the annular direction of the circumferential surface.   The sum of the annular lengths of the respective circumferential surfaces of the serrated irregularities is 20% or more of the annular length of the guide surface on the raceway side or the guide surface on the cage side. Item 2. A rolling bearing according to Item 2.

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