JP2009047294A - Roller bearing for reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a roller bearing for a reduction gear which can improve lubrication performance between pockets of a ball bearing cage and rollers, and the lubrication performance of the bearing as a whole. <P>SOLUTION: This roller bearing 1 comprises the ball bearing cage 2 in which a plurality of the long-window shaped pockets 4 extending in axial directions are formed so as to align in the circumferential direction, and a plurality of the balls 6 held at the pockets 4. Grooves 4aa are formed at ends 4a of the pockets 4 of the ball bearing cage 2 in the axial directions. The roller bearing 1 is interposed between the external diameter face of a crank shaft in the reduction gear and the internal diameter face of a gear which is eccentrically driven by the crank shaft, and the external diameter face and the internal diameter face are made to serve as transfer faces of the rollers 6. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a speed reducer roller bearing used for supporting a crankshaft in a speed reducer.

  There is an eccentric oscillating gear speed reducer configured to eccentrically move an external gear by eccentric movement of a crankshaft and to rotate a pin gear that is an internal gear that meshes with the external gear (for example, Patent Document 1). 2). In this type of gear reducer, a roller bearing is used as the bearing 41 that supports the crank portions 60a and 60b of the crankshaft 60 as shown in FIG. 11, but a high load capacity is required for such a roller bearing. Is done.

  Therefore, as a roller bearing that meets such requirements, the cage for holding the roller is composed of a pair of parallel ring-shaped flange portions and a plurality of column portions that connect both flange portions at the outer periphery. And what increased the number of the rollers to hold | maintain (for example, patent document 3) is used.

However, in the case of the roller bearing used in the crank part of the reduction gear described above, the use conditions are severe, and an oil film between the pocket end surfaces of the cage is cut, and drilling wear may occur on the pocket end surfaces.
Further, since the number of rollers is large and the space volume in the bearing is small, it is difficult for the lubricant to flow in. In addition, as shown in FIG. 11, there is a shaft between the outer diameter surface of the cage 42 and the inner diameter surface of the external gears 51 and 52, or between the inner diameter surface of the cage flange portion 42a and the crankshaft 60. There are only slight gaps in the width direction. In addition, the gap between the inner diameter surface of the cage flange portion 42a and the crankshaft 60 supports a portion other than the washer 53 that restricts the axial movement of the roller bearing 41 and the crank portions 60a and 60b of the crank bearing 60. It is closed by inner rings 54 and 55 of the tapered roller bearing. For these reasons, it is difficult for the lubricant to flow into the roller bearing 41.
For these reasons, the oil film is cut off at the crank portion of the speed reducer, and wear or peeling is likely to occur.

In this type of roller bearing, as a lubricant with improved lubrication performance, a cage portion is provided with a stealing portion (for example, Patent Document 4), and a roller guide surface of the cage pocket is provided with a groove (for example, Patent documents 5), those having a groove on the width surface of the cage (for example, patent document 6), and those having a groove on the outer diameter surface (for example, patent document 7) have been proposed.
JP-A-7-299791 JP 2006-29393 A JP 2000-55145 A Japanese Patent Laid-Open No. 11-108065 JP 2000-18258 A JP 2004-52796 A JP 2000-352423 A

  However, in the roller bearings having the configurations disclosed in Patent Documents 2 to 7, drilling wear occurs because lubrication at the end face of the cage pocket cannot be improved even if the lubrication performance can be improved. there is a possibility.

  An object of the present invention is to provide a speed reducer roller bearing capable of improving the lubrication performance between the end faces of the cage pocket and the lubrication performance of the entire bearing.

A roller bearing for a reduction gear according to a first aspect of the present invention includes a cage in which a plurality of long window-shaped pockets extending in the axial direction are formed side by side in the circumferential direction, and a plurality of rollers held in the pockets. A reduction gear having the outer diameter surface and the inner diameter surface as a rolling surface of the roller interposed between an outer diameter surface of a crankshaft of the reduction gear and an inner diameter surface of a gear that is eccentrically moved by the crankshaft. In the machine roller bearing, a groove is provided in an end portion in the axial direction of the pocket of the cage.
According to this configuration, since the groove is provided in the axial end portion of the cage pocket, the lubrication performance between the pocket end surface in the axial direction can be improved, and drilling wear due to poor lubrication can be generated. Can be prevented. Further, the lubricant easily flows into the bearing, and the overall lubrication performance can be improved.

A roller bearing for a reduction gear according to a second aspect of the present invention includes a cage in which a plurality of long window-shaped pockets extending in the axial direction are formed side by side in the circumferential direction, and a plurality of rollers held in the pockets. A reduction gear having the outer diameter surface and the inner diameter surface as a rolling surface of the roller interposed between an outer diameter surface of a crankshaft of the reduction gear and an inner diameter surface of a gear that is eccentrically moved by the crankshaft. In the machine roller bearing, a protrusion is provided at an end portion in the axial direction of the pocket of the cage.
According to this configuration, since a gap through which the lubricant flows can be ensured between the roller end surface that contacts the projection in the pocket of the cage and the axial end surface, the lubricating performance between the axial end surface of the pocket is improved. And drilling wear due to poor lubrication can be prevented. Further, the lubricant easily flows into the bearing, and the overall lubrication performance can be improved.

  In this invention, you may provide a stealing part in the corner part of the said pocket. In the case of this configuration, the lubricating performance between the pockets in the axial direction end face can be further improved, and the lubricating performance of the entire bearing can be further improved.

  In this invention, you may guide the said roller in the inner surface of the said pocket, and you may provide a groove | channel in the roller guide surface of each pillar part between adjacent pockets. Also in this configuration, the lubricating performance of the entire bearing can be further improved.

  In this invention, you may provide the groove | channel which faces the outer side of an axial direction, or the notch part which faces an inner diameter side in the circumferential direction several places of the annular part used as the edge part of the said holder | retainer. Also in this configuration, the lubricating performance of the entire bearing can be further improved.

  In the present invention, a spiral groove may be provided on the outer diameter surface of the cage. Also in this configuration, the lubricating performance of the entire bearing can be further improved.

  In this invention, each pillar part between the adjacent pockets of the cage has a shape in which the central part in the axial direction is recessed toward the inner diameter side, and the central part is on the outer diameter side from the pitch circle of the roller arrangement. It is good also as what is located in. In the case of this configuration, the cage can be configured to have a high rigidity and can cope with a high load.

A roller bearing for a reduction gear according to a first aspect of the present invention includes a cage in which a plurality of long window-shaped pockets extending in the axial direction are formed side by side in the circumferential direction, and a plurality of rollers held in the pockets. A reduction gear having the outer diameter surface and the inner diameter surface as a rolling surface of the roller interposed between an outer diameter surface of a crankshaft of the reduction gear and an inner diameter surface of a gear that is eccentrically moved by the crankshaft. In the machine roller bearing, since the groove is provided in the axial end portion of the pocket of the cage, the lubrication performance between the end faces of the cage pocket and the lubrication performance of the entire bearing can be improved.
A roller bearing for a reduction gear according to a second aspect of the present invention is the roller bearing used in the reduction gear as described above, because the protrusion is provided at the axial end of the pocket of the cage. It is possible to improve the lubrication performance between the end faces of the vessel pocket and the lubrication performance of the entire bearing.

A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 (A) shows a partial cross-sectional view of the roller bearing for reduction gears of this embodiment, and FIG. 1 (B) shows a partial side view of the cage. This roller bearing 1 is used in an eccentric oscillating speed reducer 21 shown in a sectional view in FIG. 2, and includes a ring-shaped cage 2 in which a plurality of pockets 4 are formed side by side in the circumferential direction. And a plurality of rollers 6 such as needle rollers held in the pocket 4 of the cage 2.
As shown in FIG. 3, the roller bearing 1 has outer diameter surfaces of crank portions 30 a and 30 b of the crankshaft 30 in the reduction gear 21 (FIG. 2) and external gears 31 and 32 that are eccentrically moved by the crankshaft 30. Between the outer diameter surfaces of the crank portions 30a and 30b of the crankshaft 30 and the inner diameter surfaces of the crank portion through holes 31a and 32a. It is what.

As shown in FIG. 1, the cage 2 includes a plurality of long window-shaped pockets 4 extending in the axial direction and arranged in the circumferential direction, and a pair of annular portions 2 a serving as both ends, and adjacent pockets 4. It is comprised with the pillar part 5 which connects the annular part 2a of both sides between. The annular portions 2a on both sides are composed of a cylindrical portion 2aa whose inner and outer peripheral surfaces are the same cylindrical surface as the column portion 5, and a flange portion 3 extending from the cylindrical portion 2aa to the inner diameter side. The cage 2 is made of a metal such as a pressed product of a steel plate or a synthetic resin.
As shown in FIG. 1B, two grooves 4aa that are recessed toward the end of the cage are provided at both axial ends 4a and 4a of the pocket 4, respectively. The two grooves 4aa are arranged in the circumferential direction of the cage 2. These grooves 4aa are formed in the cylindrical portion 2aa of the annular portion 2a of the cage 2, and are opened between the inner and outer peripheral surfaces of the cylindrical portion 2aa.
The roller 6 supported by the pocket 4 is inserted into the pocket 4 so that its axis (pitch circle center PCD) is located on the inner diameter side of the column part 5 as shown in FIG.

  An example of an eccentric oscillating speed reducer 21 in which the roller bearing 1 is used is shown in FIG. The speed reducer 21 decelerates and transmits the rotation of the input shaft 22 connected to a rotation shaft (not shown) such as a motor to a rotary cylindrical body 23 that is an output shaft arranged concentrically with the input shaft 22. To do. The rotating cylinder 23 is disposed on the outer peripheral side of a substantially columnar support 24 that is concentrically arranged and fixed to another fixing member (not shown), and supports the support 24 via a ball bearing 27. Is supported rotatably. The support 24 has two discs 25, 26 arranged side by side in the axial direction via three pillar portions 25 a provided on one surface of one disc 25 so as to project at equal positions in the circumferential direction. They are connected and integrated by fastening means such as bolts 28. The support 24 has a shaft insertion hole 29 at its axis, and the input shaft 22 is loosely fitted into the shaft insertion hole 29.

  Three crankshafts 30 are arranged on the support 24 in parallel with the axis thereof at equidistant positions in the circumferential direction, and both ends of the crankshaft 30 are supported via tapered roller bearings 34 and 35, respectively. The discs 25 and 26 of the body 24 are rotatably supported. An intermediate gear 37 is provided at one end of the crankshaft 30, and this intermediate gear 37 meshes with a pinion 36 formed at one end of the input shaft 22. Thereby, the rotation of the input shaft 22 is decelerated and transmitted to the crankshaft 30.

  The crankshaft 30 has a pair of crank portions 30a and 30b aligned in the axial direction at the intermediate portion thereof, and both the crank portions 30a and 30b are eccentric from the axis of the crankshaft 30 by a predetermined amount, and the eccentric position thereof is They are designed to have a phase difference of 180 ° from each other. External gears 31 and 32 are supported on the crank portions 30a and 30b via the roller bearing 1 shown in FIG. Specifically, the external gears 31 and 32 have crank portion through holes 31a and 32a that penetrate in the axial direction at positions corresponding to the respective crank shafts 30 in the circumferential direction. The roller bearing 1 is interposed with the inner diameter surface and the outer diameter surfaces of the crank portions 30a and 30b as rolling surfaces. Further, these external gears 31 and 32 have three loose fitting holes 31b and 32b in which the respective pillar portions 25a of the disk 25 of the support 24 are loosely fitted at equal positions in the circumferential direction. The eccentric gears 31 and 32 are allowed to swing eccentrically due to the rotation of the crankshaft 30.

  On the other hand, a pin gear 33 constituted by arranging a plurality of axially oriented pins in the circumferential direction on an inner diameter surface of the rotating cylindrical body 23 facing the outer teeth of the outer teeth of the outer gears 31 and 32 is an outer gear. 31 and 32 are provided so as to be able to mesh with each other. The pin gear 33 has one more tooth than the external gears 31 and 32.

  The speed reduction operation of the speed reducer 21 is performed as follows. The rotation of the input shaft 22 connected to a rotating shaft such as a motor is transmitted at a reduced speed to the crankshaft 30 from the pinion 36 at the shaft end through an intermediate gear 37 provided at the shaft end of the crankshaft 30. When the crankshaft 30 is rotated, the external gears 31 and 32 supported by the crank portions 30a and 30b via the roller bearing 1 are eccentrically oscillated as the crank portions 30a and 30b are eccentrically rotated. At this time, the external teeth on the outer periphery of the external gears 31 and 32 perform an operation of getting over the pin of the pin gear 33 on the inner diameter surface of the rotating cylindrical body 23, whereby the rotating cylindrical body 23 is pushed, The pin gear 33 rotates by one pitch. Thereby, the rotation of the crankshaft 30 is decelerated and transmitted to the rotating cylindrical body 23 that is the output shaft.

  A part of the speed reducer 21 of FIG. 2 is enlarged and shown in FIG. As shown in the figure, the roller bearing 1 is interposed between the outer diameter surfaces of the crank portions 30 a and 30 b of the crankshaft 30 and the inner diameter surfaces of the through holes 31 a and 32 a of the external gears 31 and 32. In this roller bearing 1, between the outer diameter surface of the cage 2 and the inner diameter surfaces of the through holes 31a and 32a of the external gears 31 and 32, or between the inner diameter surface of the cage flange portion 3 and the crank portions 30a and 30b. There is only a small gap between them in the axial width dimension. In addition, the gap between the inner diameter surface of the cage flange portion 3 and the crank portions 30a and 30b is other than the washers 38 and 39 that restrict the axial movement of the roller bearing 1 and the crank portions 30a and 30b of the crank bearing 30. It is closed by inner rings 34a, 35a of tapered roller bearings 34, 35 that support the portions. For these reasons, the lubricant is difficult to flow into the roller bearing 1.

  However, according to the roller bearing 1 of this embodiment, as shown in FIG. 1 (B), since the groove 4aa is provided at the axial end of the pocket 4 of the cage 2, the axial end surface of the pocket 4 is provided. However, the lubricating performance with 6 is improved. For this reason, occurrence of drilling wear due to poor lubrication can be prevented. In addition, the lubricant easily flows into the bearing 1, and the overall lubrication performance is improved.

FIG. 4 shows another embodiment of the present invention. In this embodiment, in the roller bearing in the embodiment of FIG. 1, instead of providing the groove 4aa at the axial end of the pocket 4 of the cage 2, two protrusions 4ab are provided. These protrusions 4ab are arranged in the circumferential direction of the cage. The protrusion 4ab is, for example, a linear shape that is formed over the entire thickness of the cylindrical portion 2aa of the cage 2 and extends in the radial direction of the cage, and has a mountain shape such as a semicircular cross section. The protrusion 4ab may have a hemispherical shape or the like.
In the case of this embodiment, if the roller 6 having the same size as that of the embodiment of FIG. 1 is used, the dimension between both ends in the axial direction of the pocket 4 is set longer than that of the embodiment of FIG. That is, the dimension between the protrusions 4ab and 4ab at both ends of the pocket 4 in this embodiment is set to be equal to the dimension between both ends in the axial direction of the pocket 4 in the embodiment of FIG. Other configurations are the same as those in the embodiment of FIG.

  In the case of this embodiment as well, a gap through which the lubricant flows can be secured between the roller end surface that contacts the projection 4ab in the pocket 4 of the cage 2 and the axial end surface, so that the axial end surface 6 of the pocket 4 The lubrication performance can be improved, and drilling wear due to poor lubrication can be prevented. Further, the lubricant easily flows into the bearing 1 and the overall lubrication performance is improved.

  FIG. 5 shows still another embodiment of the present invention. In this embodiment, in the roller bearing in the embodiment of FIG. 1, the cage 2 is an M-type cage. That is, the column part 5 between the pockets 4 has a trapezoidal shape including an outer diameter side part 5a at both ends, an inclined part 5c obliquely extending from the outer diameter side part 5a to the inner diameter side, and a central inner diameter side part 5b. Formed. The column part 5 and the flange part 3 extending from the both ends of the column part 5 to the inner diameter side via the cylindrical part 2aa are configured so that the cross-sectional shape of the entire cage is substantially M-shaped. The inner diameter side portion 5b at the center of the column portion 5 is positioned on the outer diameter side with respect to the shaft center (pitch circle center PCD) of the roller 6, and does not have a function of preventing the roller 6 from dropping to the inner diameter side. Other configurations are the same as those in the embodiment of FIG.

  Thus, by making the cross-sectional shape of the cage 2 M-shaped, it is possible to achieve a highly rigid configuration and cope with a high load. The effect of improving the lubricating performance is the same as in the embodiment of FIG. Note that the same effect as described above can be obtained even when the structure in which the cross-sectional shape of the cage 2 is M-shaped is applied to the roller bearing 1 of the embodiment of FIG.

  FIG. 6 shows still another embodiment of the present invention. In this embodiment, in the roller bearing 1 in the embodiment of FIG. 1, the stealing portions 4 c are provided at the four corners of the pocket 4 of the cage 2. Each stealing portion 4c has an arcuate cutout shape. Other configurations are the same as those in the embodiment of FIG.

  In the case of this embodiment, not only the groove 4aa (FIG. 1B) is provided at the axial end of the pocket 4 of the cage 2, but also the stealing portion 4c is provided at the four corners of the pocket 4. Therefore, the lubrication performance between the pocket 4 and the axial end surface 6 can be further improved, and the lubrication performance of the entire bearing is further improved. Note that the same effect as described above can be obtained even if the structure in which the stealing portion 4c is provided at the corner of the pocket 4 is applied to the roller bearing 1 of the embodiment of FIG.

  FIG. 7 shows still another embodiment of the present invention. In this embodiment, in the roller bearing 1 in the embodiment of FIG. 1, a plurality of grooves 4ba are formed on the roller guide surface 4b of each column portion between the adjacent pockets by guiding the roller 6 on the inner surface of the pocket 4 of the cage 2. It is provided. The roller guide surfaces 4 b are side surfaces on both sides of the column portion 5. Other configurations are the same as those in the embodiment of FIG.

  In the case of this embodiment, not only the groove 4aa (FIG. 1B) is provided at the axial end of the pocket 4 of the cage 2, but also a roller guide surface for guiding the roller 6 on the inner surface of the pocket 4. Since the groove 4ba is also provided in 4b, the lubrication performance between the pocket 4 and the end surface 6 in the axial direction can be improved, and the lubrication performance of the entire bearing is further improved. Even if the structure in which the groove 4ba is provided in the roller guide surface 4b of the pocket 4 is applied to the roller bearing 1 of the embodiment of FIG. 4, the same effects as described above can be obtained.

  FIG. 8 shows still another embodiment of the present invention. In this embodiment, a spiral groove 7 is provided on the outer diameter surface of the cage 2 in the roller bearing 1 in the embodiment of FIG. In FIG. 8, hatching is applied to the area where the spiral groove 7 is formed. The spiral grooves 7 are interrupted at the both ends in the axial direction of the cage 2 and divided into a plurality of parts, but each of these spiral grooves 7 is virtually located on one spiral line. The spiral groove 7 is spaced so that two circumferential groove portions, which are each one circumferential portion of the spiral, are arranged within the width of the cage 2. Other configurations are the same as those in the embodiment of FIG.

  In the case of this embodiment, not only the groove 4aa (FIG. 1 (B)) is provided at the axial end of the pocket 4 of the cage 2, but also the helical groove 7 on the outer diameter surface of the cage 2. Therefore, the lubrication performance between the pocket 4 and the end surface 6 in the axial direction can be improved, and the lubrication performance of the entire bearing is further improved. Even if the structure in which the spiral groove 7 is provided on the outer diameter surface of the cage 2 is applied to the roller bearing 1 of the embodiment of FIG. 4, the same effect as described above can be obtained.

  FIG. 9 shows still another embodiment of the present invention. In this embodiment, in the roller bearing 1 in the embodiment of FIG. 1, notches 3a facing the inner diameter side are provided at a plurality of circumferential portions of the flange portion 3 constituting the annular portions 2a at both ends of the cage 2. It is. A plurality of cutout portions 3a are provided side by side in the circumferential direction of the cage 2, and the shape of the inner peripheral edge of the flange portion 3 is corrugated by the cutout portions 3a. The shape of the notch 3a is an arc shape or a sine curve shape, but may be any other shape. Other configurations are the same as those in the embodiment of FIG.

  In the case of this embodiment, not only grooves 4aa (FIG. 1 (B)) are provided at the axial ends of the pockets 4 of the cage 2, but also at multiple locations in the circumferential direction of the flange portion 3 of the cage 2. Since the notch 3a facing the inner diameter side is provided, the lubrication performance between the pocket 4 and the axial end surface 6 can be improved, and the lubrication performance of the entire bearing is further improved. Even if the structure in which the notch portions 3a facing the inner diameter side are provided at a plurality of locations in the circumferential direction of the flange portion 3 of the cage 2 is applied to the roller bearing 1 of the embodiment in FIG. it can.

  FIG. 10 shows still another embodiment of the present invention. In this embodiment, in the roller bearing 1 in the embodiment of FIG. 1, grooves 3 b facing outward in the axial direction are provided at a plurality of circumferential positions of the flange portion 3 constituting the annular portion 2 a at both ends of the cage 2. Is. In FIG. 10, the range in which the groove 3b is formed is hatched. The groove 3b has a shape that extends from the inner peripheral edge to the outer peripheral edge of the flange portion 3. Other configurations are the same as those in the embodiment of FIG.

  In the case of this embodiment, not only grooves 4aa (FIG. 1 (B)) are provided at the axial ends of the pockets 4 of the cage 2, but also at multiple locations in the circumferential direction of the flange portion 3 of the cage 2. Since the groove 3b facing outward in the axial direction is provided, the lubrication performance between the pocket 4 and the axial end surface 6 can be improved, and the lubrication performance of the entire bearing is further improved. Even if the structure in which the grooves 3b facing the outside in the axial direction are provided at a plurality of locations in the circumferential direction of the flange portion 3 of the cage 2 is applied to the roller bearing 1 of the embodiment of FIG. be able to.

(A) is a fragmentary sectional view of the roller bearing concerning 1st Embodiment of this invention, (B) is the partial expanded view which shows the holder | retainer of the roller bearing from the outer diameter side. It is sectional drawing of an example of the speed reducer in which the roller bearing is used. It is a partial expanded sectional view in the speed reducer. It is a partial expanded view which shows the retainer of the roller bearing concerning other embodiment of this invention. It is a partial expanded view which shows the holder | retainer of the roller bearing concerning further another embodiment of this invention. It is a partial expanded view which shows the holder | retainer of the roller bearing concerning further another embodiment of this invention. It is a partial expanded view which shows the holder | retainer of the roller bearing concerning further another embodiment of this invention. It is a partial expanded view which shows the holder | retainer of the roller bearing concerning further another embodiment of this invention. It is a side view of the roller bearing concerning further another embodiment of this invention. It is a side view of the roller bearing concerning further another embodiment of this invention. It is a principal part expanded sectional view of the reduction gear in which the conventional roller bearing is used.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Roller bearing 2 ... Cage 2a ... Ring-shaped part 2aa ... Cylindrical part 3 ... Cage flange part 3a ... Flange part notch part 3b ... Flange part groove | channel 4 ... Pocket 4a ... Pocket axial end part 4aa ... Axial end groove 4ab ... Axial end protrusion 4c ... Steal 4b ... Roller guide surface 4ba ... Roller guide surface groove 5 ... Pillar 6 ... Roller 7 ... Helical groove 21 ... Speed reducer 30 ... Crankshafts 30a, 30b ... crank portions 31, 32 ... external gears

Claims (7)

A cage comprising a plurality of long window-shaped pockets extending in the axial direction and arranged in the circumferential direction; and a plurality of rollers held in the pockets; In a roller bearing for a reduction gear, which is interposed between an inner diameter surface of a gear that is eccentrically moved by a shaft and uses the outer diameter surface and the inner diameter surface as a rolling surface of the roller,
A roller bearing for a reduction gear, wherein a groove is provided at an end portion in the axial direction of the pocket of the cage. A cage comprising a plurality of long window-shaped pockets extending in the axial direction and arranged in the circumferential direction; and a plurality of rollers held in the pockets; In a roller bearing for a reduction gear, which is interposed between an inner diameter surface of a gear that is eccentrically moved by a shaft and uses the outer diameter surface and the inner diameter surface as a rolling surface of the roller,
A roller bearing for a reduction gear, wherein a protrusion is provided at an end portion in the axial direction of the pocket of the cage.   The roller bearing for a reduction gear according to claim 1 or 2, wherein a stealing portion is provided at a corner of the pocket.   The roller for a reduction gear according to any one of claims 1 to 3, wherein the roller on the inner surface of the pocket is guided and a groove is provided on a roller guide surface of each column portion between adjacent pockets. bearing.   5. The groove that faces the outside in the axial direction or the notch portion that faces the inner diameter side is provided at a plurality of locations in the circumferential direction of the annular portion serving as an end portion in the axial direction of the retainer according to claim 1. Provided roller bearings for reduction gears.   The roller bearing for a reduction gear according to any one of claims 1 to 5, wherein a spiral groove is provided on an outer diameter surface of the cage.   In any one of Claims 1 thru | or 6, each pillar part between the pockets which the said holder | retainer adjoins is a shape where the center part of the axial direction was dented in the inner diameter side, and the said center part is a roller arrangement | sequence. A roller bearing for a reduction gear, wherein the roller bearing is located on the outer diameter side of the pitch circle.

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