JP2008151259A - Needle roller bearing cage and needle roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a needle roller bearing having high load bearing capability when bearing a high load and moment force in a restricted mounting space. <P>SOLUTION: This needle roller bearing cage 22 comprises a plurality of pockets 26 formed at predetermined circumferential spaces in a single axial line for rollingly holding a plurality of needle rollers 21. An axial center position C of at least one of the pockets 26 is different from an axial center position A of the cage 22. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a needle roller bearing retainer and a needle roller bearing, and more particularly to a needle roller bearing retainer and a needle roller bearing for supporting gears used in general industrial machines, automobile transmissions, and the like.

  The needle roller bearing is configured using a plurality of needle rollers having a length that is longer than a diameter. As shown in FIG. 11, as the needle roller bearing 100, various cage and rollers composed of these needle rollers 101 and a cage 102 that holds the needle rollers 101 have been devised (for example, patents). References 1 and 2, and Non-Patent Document 1). For example, it is used for supporting a transmission gear in an automobile transmission.

In the needle roller bearings described in these documents, the axial center position of the roller and the axial center position of the cage are the axial clearance of the pocket housing the roller and the axial center of the cage generated during processing. The positions are set to substantially the same within the range of variation in the distance from the position to the axial center position of the pocket.
Japanese Patent Laid-Open No. 2004-11657 (FIG. 3) Japanese Patent Laid-Open No. 2000-213545 (FIG. 1) “NSK Needle Bearing Product Catalog CAT.No. 1419h” NSK Ltd., 2003 (pages B12-B16)

  By the way, as shown in FIG. 12, the transmission gear 103 of the automobile transmission has a configuration in which the load point position P is shifted from the axial center position A of the cage 102 by a distance B in the axial direction. When such a transmission gear 103 is supported by the needle roller bearing 100 described above, the load distribution applied to the bearing is not uniform in the axial direction, and the gear of the bearing is caused by the radial load, the moment due to the distance B, and the moment due to the thrust load. There is a possibility that a large load is generated on the side and the gear is inclined.

  However, in the needle roller bearing 100 described above, since the axial center position C of the roller 101 is substantially the same position as the axial center position A of the cage 102, the load of the bearing against the load and moment force received by the bearing. When the capacity is insufficient, there is a problem of causing damage to the bearings and gear teeth due to a large gear inclination.

  The present invention has been made in view of the above-described circumstances, and the object thereof is to realize a high load carrying ability when a high load and a moment force are applied in a restricted installation space. An object of the present invention is to provide a needle roller bearing cage and a needle roller bearing.

The above object of the present invention can be achieved by the following constitution.
(1) A needle roller bearing retainer that has a plurality of pockets that are formed in a single row in the axial direction at a predetermined interval in the circumferential direction and that hold a plurality of needle rollers in a rollable manner. ,
The single row needle roller bearing cage is characterized in that at least one axial center position of the pocket is different from the axial center position of the cage.
(2) The needle roller bearing according to (1), wherein all axial center positions of the plurality of pockets are shifted to one side with respect to the axial center position of the cage. Cage.
(3) The plurality of pockets have one side pocket whose axial center position is shifted to one side with respect to the axial center position of the cage, and the axial center position thereof is the axial center position of the cage. The needle roller bearing retainer as set forth in (1), further comprising: the other side pocket shifted to the other side.
(4) The needle roller bearing retainer according to (1), wherein the number of the one side pockets is equal to the number of the other side pockets.
(5) The needle roller bearing retainer according to (1) or (2), wherein the retainer has a reverse assembly preventing function capable of discriminating directionality in the axial direction of the retainer.
(6) A needle roller bearing comprising: the cage according to any one of (1) to (5); and the plurality of needle rollers held in the pocket.

  According to the needle roller bearing retainer and the needle roller bearing of the present invention, since at least one axial center position of the pocket is different from the axial center position of the cage, the load is applied to the axial center position of the pocket. By shifting in a stricter direction, the load due to the moment applied to the bearing can be reduced, and the surface pressure and gear inclination can be reduced. For this reason, when a high load and a moment force are applied in a restricted installation space, a high load capacity can be realized.

  Hereinafter, a needle roller bearing retainer and a needle roller bearing according to each embodiment of the present invention will be described in detail with reference to the drawings.

(First embodiment)
FIG. 1 is a sectional view of a manual vehicle transmission using a needle roller bearing according to the present embodiment. In the transmission shown in FIG. 1, an input shaft 2 is rotatably supported by bearings 3 and 4 (with a left end via a third drive gear 11) in a housing 1 that is only partially shown, while an intermediate shaft 5 and a fixed shaft 6 are supported in parallel to the housing 1. On the input shaft 2, it is movable in the axial direction with respect to the input shaft 2 by spline coupling, but is rotatable through a first drive gear 7 that rotates integrally and a radial needle roller bearing 8. A second drive gear 9 that is supported and a third drive gear 11 that is rotatably supported via a radial bearing (which may be a radial needle roller bearing) 10 are arranged. The synchronizing device 17 that is movable in the axial direction with respect to the input shaft 2 by being spline-coupled to the input shaft 2, but rotates integrally with the second drive gear 9 or the third drive gear 11. Engageable.

  On the intermediate shaft 5, a first driven gear 12a, a second driven gear 12b that can mesh with the first drive gear 7, a third driven gear 12c that meshes with the second drive gear, and a third drive gear. A driven gear unit 12 that forms a fourth driven gear 12 d meshed with the gear 11 is rotatably supported by radial needle roller bearings 18 and 19. The first driven gear 12 a of the driven gear unit 12 meshes with an output gear 16 that is rotatably supported on the fixed shaft 6 via a radial bearing 15. The output gear 16 is connected to wheels via a power train (not shown) so that power can be transmitted.

  It is assumed that the input shaft 2 is rotated by receiving power from an engine (not shown). The state shown in FIG. 1 is a so-called neutral state, and such a transmission is in a state where power is not transmitted to a wheel (not shown). Here, when a shift fork (not shown) is operated, the synchronizing device 17 is moved to the left in the axial direction in FIG. 1 and is engaged with the internal teeth 11 a of the third driving gear 11, the third driving gear 11 is moved to the synchronizing device 17. And rotate integrally with the input shaft 2. As a result, the driven gear unit 12 in which the fourth driven gear 12d is engaged with the third drive gear 11 is rotated according to the gear ratio thereof, and is decelerated (corresponding to the first speed here). Is transmitted to the output gear 16.

  Subsequently, when a shift fork (not shown) is operated, the synchronization device 17 is moved to the right in the axial direction in FIG. 1 and engages with the internal teeth 9 a of the second drive gear 9, the second drive gear 9 is synchronized with the synchronization device 17. And rotate integrally with the input shaft 2. As a result, the driven gear unit 12 having the third driven gear 12c meshed with the second drive gear 9 is rotated according to the gear ratio thereof, and the decelerated power (corresponding to the second speed here) is generated. It is transmitted to the output gear 16.

  Further, a shift fork (not shown) is operated, and the synchronization device 17 is returned to a position where it does not engage with either the second drive gear 9 or the third drive gear 11 (the state shown in FIG. 1). When the integrally driven first drive gear 7 is moved to the left in the axial direction in FIG. 1, the second drive gear 12b is engaged with the first drive gear 7, whereby the driven gear unit 12 is engaged with the first drive gear. 7 and the second driven gear 12 b are rotated according to the gear ratio, and the decelerated power (corresponding to the third speed here) is transmitted to the output gear 16. The above is the shift operation for shifting up, and the shifting operation for shifting down is the opposite.

  As shown in FIG. 2, the radial needle roller bearing 8 includes a plurality of needle rollers 21 and a cage-type cage 22 that holds the rollers 21 at predetermined intervals. 2 is arranged between the inner peripheral surface of the drive gear 9. As shown in FIG. 3, the retainer 22 includes a pair of ring-shaped portions 23 and 24 and a plurality of column portions 25 that connect them. Thereby, a plurality of pockets 26 are formed at a predetermined interval in the circumferential direction and in a single row in the axial direction by the pair of ring-shaped portions 23, 24 and the adjacent column portion 25. Hold it rollable. The cage 22 is regulated in the axial direction by the flange portion of the input shaft 2 and the regulating member 40.

  Further, the ring-shaped portion 23 is formed longer in the axial direction than the ring-shaped portion 24 on the load point position side of the second drive gear 9. For this reason, all the axial center positions C of the plurality of pockets 26, that is, the axial center positions of all the needle rollers 21 are different from the axial center position A of the cage 22. The distance D).

  By configuring the needle roller bearing 8 in this way, even if the load point position P of the second drive gear 9 is shifted from the axial center position A of the cage 22 by the distance B in the axial direction, the needle Since the center position in the axial direction of the tapered roller 21 is shifted to the load point position where the load becomes severe, the load due to the moment applied to the bearing is reduced, and the surface pressure and gear are compared with the conventional bearing specifications as shown in FIG. The inclination of the can be reduced.

  In addition, the cage 22 has a reverse assembly preventing function capable of discriminating the directionality of the cage 22 in the axial direction. Identification processing such as a marking mark 27 (see FIG. 3) and coloring is performed.

  Therefore, according to the needle roller bearing retainer 22 and the needle roller bearing 8 of the present embodiment, all the axial center positions C of the pocket 26 are different from the axial center position A of the retainer 22, and the pocket 26. By shifting the axial center position C to the load point position side of the second drive gear 9 where the load becomes severe, the load due to the moment applied to the bearing is reduced, and the surface pressure and the gear inclination can be reduced. Further, since the pockets 26 are formed in a single row in the axial direction, the cost can be reduced as compared with the double row bearings, and a high load is applied when a high load or moment force is applied in a restricted installation space. Load capacity can be realized.

  In the above-described embodiment, the identification process using the marking mark 27 is performed. However, the reverse assembly prevention function is not limited to this. For example, the retainer 22a of the first modification shown in FIG. In addition, an outward flange portion 28 may be provided on the inner tooth side (the other side) of the second drive gear 9 to prevent reverse assembly. Further, as in the cage 22b of the second modification shown in FIG. 5, inward flange portions 29a and 29b are provided on both sides in the axial direction, and the inward flange portion 29a on the inner tooth side of the second drive gear 9 is a flange portion. It may be configured longer than 29b in the radial direction to prevent reverse assembly.

(Second Embodiment)
Next, with reference to FIGS. 4-6, the needle roller bearing retainer and needle roller bearing which are 2nd Embodiment of this invention are demonstrated. In addition, about the part which overlaps with 1st Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  As shown in FIG. 4, the needle roller bearing 8 of the present embodiment is different from that of the first embodiment in the configuration of the cage. That is, in the needle roller bearing retainer 30, the axial center position C1 is shifted from the axial center position A of the retainer 30 by the distance D to the load point position side (one side) of the second drive gear 9. One side pocket 26a and the other side pocket 26a in which the axial center position C2 is shifted to the inner tooth side (the other side) of the second drive gear 9 by a distance D with respect to the axial center position A of the cage 30; It is formed alternately in the circumferential direction. Therefore, the number of the one side pockets 26a is equal to the number of the other side pockets 26b.

As a result, the axial center positions C1 and C2 of the one-side and other-side pockets 26a and 26b are different from the axial center position A of the cage 30, and the axial center position C1 of the one-side pocket 26a has a severe load. By shifting to the load point position side of the drive gear 9, the load due to the moment applied to the bearing is reduced by the needle rollers 21 held in the one side pocket 26a, and the surface pressure and the gear inclination can be reduced. it can. Further, since the same number of the one side and the other side pockets 26a and 26b are alternately arranged in the circumferential direction, the needle roller bearing 8 has no directionality and can be assembled from either side, so that the first embodiment Thus, it is not necessary to provide a reverse assembly prevention function as described above, and the assembling property is improved and the cost can be further reduced.
Other configurations and operations are the same as those in the first embodiment.

  In the present embodiment, the one side pocket and the other side pocket 26a, 26b are alternately arranged in the circumferential direction. However, like the cage 30a of the first modification shown in FIG. May be arranged alternately, or a plurality of them may be provided. Further, like the cage 30b of the second modification shown in FIG. 7, the axial intermediate position C3 is the same position as the axial intermediate position A of the cage 22 between the one side pocket 26a and the other side pocket 26b. A pocket 26c may be formed. Since the needle roller bearing 8 having these cages 30a and 30b also has no directionality, it is not necessary to provide a reverse assembly preventing function.

  Note that the needle roller bearing retainer and the needle roller bearing of the present invention are not limited to the above-described embodiments, and can be appropriately modified and improved.

  The cage for a needle roller bearing according to the present invention may be configured so that at least one axial center position of the pocket is different from the axial center position of the cage in a configuration in which the pockets are formed in a single row in the axial direction. The invention is not limited to the above embodiment.

  Moreover, the reverse assembly prevention function of the cage is not limited to the one in which all the axial center positions of the pockets are different from the axial center position of the cage as in the first embodiment, but to have directionality in the axial direction. This is applied when pockets are formed.

  Furthermore, the needle roller bearing of the present invention is applied to the needle roller bearing 8 interposed between the input shaft 2 and the second drive gear 9 shown in FIG. 1, but the intermediate shaft 5 and the driven gear unit. The present invention can also be applied to the needle roller bearings 18 and 19 interposed between them. Furthermore, the needle roller bearing of the present invention can be applied not only to a manual transmission but also to an automatic multi-stage transmission.

  Here, using the needle roller bearing of the first embodiment shown in FIG. 3 and the conventional needle roller bearing shown in FIG. 11, the roller contact surface pressure distribution and the gear inclination were tested. The radial load applied to the gear was 14000 N, the cage was 45 mm in inner diameter, 51 mm in outer diameter, 30 mm in width, the roller was 3 mm in diameter and 19.8 mm in width, and the number of rollers was 28.

  Further, in the conventional needle roller bearing shown in FIG. 11, the axial center position of the cage and the axial center position of the needle roller are the same position, and the distance from these positions to the load point position of the gear is determined. In the needle roller bearing of the first embodiment shown in FIG. 3, the distance (BD) from the axial center position of the needle roller to the load point position of the gear was 4 mm and 3 mm.

  FIG. 10 shows the roller contact surface pressure distribution, and Table 1 shows the maximum surface pressure and the gear inclination ratio. Here, the inclination ratio is the inclination of the specification of the first embodiment / the inclination of the conventional specification. As a result, it is understood that the maximum surface pressure is reduced and the gear inclination is reduced by shifting the axial center position of the needle roller, that is, the axial center position of the pocket to the load point position side.

1 is a cross-sectional view of a manual vehicle transmission using a needle roller bearing according to a first embodiment of the present invention. FIG. 3 is a cross-sectional view of a main part in the vicinity of a second drive gear of the vehicle transmission of FIG. 1. The needle roller bearing which is 1st Embodiment of this invention is shown, (a) is the perspective view, (b) is the front view. It is principal part sectional drawing of the 2nd drive gear vicinity in which the needle roller bearing which is the 1st modification of 1st Embodiment of this invention was integrated. It is principal part sectional drawing of the 2nd drive gear vicinity in which the needle roller bearing which is the 2nd modification of 1st Embodiment of this invention was integrated. It is principal part sectional drawing of the 2nd drive gear vicinity in which the needle roller bearing which is 2nd Embodiment of this invention was integrated. The needle roller bearing which is 2nd Embodiment of this invention is shown, (a) is the perspective view, (b) is the front view. The needle roller bearing which is the 1st modification of 2nd Embodiment of this invention is shown, (a) is the perspective view, (b) is the front view. It is a front view of the needle roller bearing which is the 2nd modification of 2nd Embodiment of this invention. It is a roller contact surface pressure distribution map of 1st Embodiment and the needle roller bearing of a conventional specification. It is a perspective view of a conventional needle roller bearing. It is principal part sectional drawing which shows the state in which the needle roller bearing of the conventional specification was integrated between the gear and the axis | shaft.

Explanation of symbols

8 Needle Roller Bearing 21 Needle Roller 22, 22a, 22b, 30, 30a, 30b Cage (Cage Roller Bearing Cage)
23, 24 Ring-shaped part 25 Column part 26 Pocket 27 Stamp mark (reverse assembly prevention function)
26a One side pocket (pocket)
26b The other side pocket (pocket)

Claims (6)

A needle roller bearing retainer having a plurality of pockets that are formed in a single row in the axial direction at a predetermined interval in the circumferential direction and each hold a plurality of needle rollers in a rollable manner,
The single row needle roller bearing cage is characterized in that at least one axial center position of the pocket is different from the axial center position of the cage.   2. The needle roller bearing retainer according to claim 1, wherein all axial center positions of the plurality of pockets are shifted to one side with respect to the axial center position of the retainer.   The plurality of pockets have an axial center position shifted to one side with respect to the axial center position of the cage, and an axial center position thereof with respect to the axial center position of the cage. 2. The needle roller bearing retainer according to claim 1, further comprising: the other side pocket shifted to the other side.   The number of said one side pockets and the number of said other side pockets are equal, The needle roller bearing retainer of Claim 1 characterized by the above-mentioned.   The needle roller bearing retainer according to claim 1 or 2, wherein the retainer has a reverse assembly prevention function capable of discriminating directionality in the axial direction of the retainer.   A needle roller bearing comprising: the cage according to any one of claims 1 to 5; and the plurality of needle rollers held in the pocket.

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