JP2023169748A - Conical roller bearing - Google Patents

Abstract

To provide a conical roller bearing that has a holder equipped with a function suppressing breakage due to shortage of oil amount.SOLUTION: A conical roller bearing 1 is equipped with an inner ring 2, an outer ring 3, a plurality of conical rollers 4 rolling and contacting with an inner ring raceway 21 and an outer ring raceway 31, and an annular holder 5 that has a plurality of pockets 9 storing the conical rollers 4. The plurality of pockets 9 have a small-diameter side side surface 6a opposite to a small-diameter side end surface 41 of a conical roller 4 to be stored, a large-diameter side side surface 7a opposite to a large-diameter side end surface 42, and a groove portion 10 formed on the large-diameter side side surface 7a. The groove portion 10 is a herringbone groove 10 that includes a plurality of V-shaped grooves 11, and in which the plurality of V-shaped grooves 11 are arranged aligned in a circumferential direction of the large-diameter side side surface 7a while turning top portions 11c of the V-shaped grooves 11 in the circumferential direction of the large-diameter side side surface 7a.SELECTED DRAWING: Figure 4

Description

The present disclosure relates to tapered roller bearings.

Patent Document 1 discloses a tapered roller bearing. A tapered roller bearing includes an inner ring, an outer ring, a plurality of tapered rollers, and an annular retainer. The cage has a plurality of pockets for accommodating tapered rollers, and holds the plurality of tapered rollers at intervals in the circumferential direction. The cage serves as a separator that prevents adjacent tapered rollers from coming into contact with each other.

For tapered roller bearings, resin cages are increasingly being used. A resin cage has a higher degree of freedom in design, such as shape, than conventional metal cages. For this reason, in recent years, consideration has been given to providing cages with functions other than the role of tapered roller separators.

Japanese Patent Application Publication No. 2013-221592

In tapered roller bearings, the tapered rollers may seize immediately after operation due to insufficient oil. In tapered roller bearings, it is desirable to prevent damage caused by such insufficient oil amount.

Therefore, an object of the present disclosure is to provide a tapered roller bearing having a retainer that has a function of suppressing damage caused by insufficient oil amount.

The tapered roller bearing of the present disclosure includes an inner raceway, a small flange provided on one axial side of the inner raceway, and a large flange provided on the other axial side of the inner raceway on the outer circumferential side. an outer ring having an outer ring raceway on the inner periphery side, a plurality of tapered rollers that roll into contact with the inner ring raceway and the outer ring raceway, and an annular retainer having a plurality of pockets for accommodating the tapered rollers. each of the plurality of pockets has a small diameter side surface facing the small diameter end surface of the tapered roller to be accommodated, a large diameter side surface facing the large diameter side end surface of the tapered roller to be accommodated, and the large diameter side surface. a groove portion formed in a groove, the groove portion including a plurality of V-shaped grooves having a V-shaped configuration when viewed from a direction perpendicular to the large-diameter side surface, and a top portion of the V-shaped groove; This is a herringbone groove in which a plurality of the V-shaped grooves are arranged side by side in the circumferential direction of the large-diameter side surface while the grooves are directed in the circumferential direction of the large-diameter side surface.

According to the tapered roller bearing, lubricating oil can be stored on the large-diameter side surface of the cage by the groove configured as a herringbone groove, and when the tapered roller bearing is not in operation, lubricating oil can be stored on the large-diameter side surface. It becomes possible to hold. In this case, immediately after the tapered roller bearing starts operating, it becomes possible to supply the lubricating oil held on the large-diameter side surface to the tapered rollers and the inner ring, thereby suppressing damage to the tapered rollers due to insufficient oil quantity. can.

Further, in the tapered roller bearing of the present disclosure, the herringbone groove has the top portion facing a first direction in the circumferential direction of the large diameter side surface and is arranged on the outside of the large diameter side surface in the radial direction. the first V-shaped groove, the top of which faces in a second direction in the circumferential direction of the large-diameter side surface, and the second V-shaped groove, which is disposed radially inside the large-diameter side surface; It is preferable that it includes a letter-shaped groove.
According to this configuration, it is possible to supply lubricating oil to the tapered rollers from the grooves regardless of the rotation direction of the tapered rollers.

Further, in the tapered roller bearing of the present disclosure, the herringbone groove is located in the first V-shaped groove located on the radially outer side of the large diameter side surface and on the radially inner side of the large diameter side surface. and a second V-shaped groove, in the radial direction of the large-diameter side surface, the width of the first V-shaped groove formation area is equal to the width of the second V-shaped groove formation area. It is preferable if it is smaller than that.
According to this configuration, it is possible to make the dynamic pressure generated when the tapered roller rotation direction is the first direction and the dynamic pressure generated when the rotation direction is the second direction to be about the same level. becomes.

Further, in the tapered roller bearing of the present disclosure, the retainer includes a small diameter annular body provided on one side in the axial direction, a large diameter annular body provided on the other side in the axial direction, the small diameter annular body and the large diameter annular body. and a plurality of columns connecting the columns, and preferably a recessed portion is provided on the radially outer side of the column.
According to this configuration, when the tapered roller bearing is not in operation, lubricating oil can be stored in the recessed portion located at a position that is not an oil reservoir. Moreover, according to the cage having the recessed portion, it is possible to make it easier for the lubricating oil to flow from the column toward the large diameter side end surface.

According to the present disclosure, the cage of the tapered roller bearing makes it possible to suppress damage caused by a lack of oil in the tapered roller bearing.

1 is a schematic cross-sectional view showing a tapered roller bearing of the present disclosure. It is a perspective view showing a cage. FIG. 3 is a partial cross-sectional view of the cage at a position including the central axis. It is a partial sectional view showing the circumference of a pocket and a groove part. It is a partial schematic diagram which shows the groove part based on 1st Embodiment. It is a schematic diagram showing the flow of lubricating oil in the groove part concerning a 1st embodiment. FIG. 3 is a partial cross-sectional view showing the positional relationship between the large-diameter end face of the tapered roller and the groove. FIG. 3 is a partial cross-sectional view showing the positional relationship between the large-diameter end face of the tapered roller and the groove. It is a partial schematic diagram which shows the groove part based on 2nd Embodiment. It is a partial schematic diagram which shows the groove part based on 3rd Embodiment.

[Configuration of tapered roller bearing]
FIG. 1 is a schematic cross-sectional view showing a tapered roller bearing of the present disclosure. FIG. 2 is a perspective view of the cage. FIG. 3 is a partial cross-sectional view of the cage at a position including the central axis. FIG. 4 is a partial cross-sectional view showing the periphery of the pocket and the groove. Note that FIG. 4 is a cross-sectional view taken along line II in FIG. 3, but for convenience of explanation, the phase around the central axis is changed in FIGS. 3 and 4. Here, the configuration of the tapered roller bearing 1 of the present disclosure will be explained based on the tapered roller bearing 1 shown in FIG. The tapered roller bearing 1 shown in FIG. , and an annular cage 5 that holds these tapered rollers 4.

The terms "axial direction", "radial direction", and "circumferential direction" in each description of the inner ring 2, outer ring 3, and cage 5 will be defined. The “axial direction” is a direction along the center line of each of the inner ring 2, outer ring 3, and retainer 5. Note that the axial direction also includes a direction parallel to the center line. The "radial direction" is a direction perpendicular to each center line. The "circumferential direction" is a direction along a circle centered on each center line. In each figure, the code of the center line of the inner ring 2, the outer ring 3, and the cage 5 in a state where the center lines coincide with each other is designated as "C0".

The terms “axial direction,” “radial direction,” and “circumferential direction” in the description of the tapered rollers 4 will be defined. The “axial direction” of the tapered rollers 4 is a direction along the center line C1 of the tapered rollers 4. In order to distinguish it from the axial direction of the inner ring 2, outer ring 3, and cage 5, the axial direction of the cage 5, etc. is simply referred to as the "axial direction", and the axial direction of the tapered rollers 4 is sometimes referred to as the "roller axial direction". be. Note that the roller axial direction also includes a direction parallel to the center line C1. The "radial direction" is a direction perpendicular to the center line C1 of the tapered roller 4, and is sometimes referred to as the "roller radial direction." The "circumferential direction" is a direction along a circle centered on the center line C1 of the tapered roller 4, and can be referred to as the "roller circumferential direction."

The inner ring 2 is an annular member formed using bearing steel, machine structural steel, or the like. The inner ring 2 has a tapered inner ring raceway 21 on its outer peripheral side. The inner ring 2 has a small flange 22 provided on one side in the axial direction of the inner ring raceway 21 (the left side in FIG. 1A, the right side in FIG. 1B), and the other side in the axial direction of the inner ring raceway 21 (the right side in FIG. 1A, the right side in FIG. 1B). In the figure, the large flange portion 23 is provided on the left side). Each of the small flange portion 22 and the large flange portion 23 protrudes radially outward.

The outer ring 3 is an annular member formed using bearing steel, machine structural steel, or the like. The outer ring 3 has a tapered outer ring raceway 31 on its inner peripheral side.

The tapered roller 4 is a truncated cone-shaped member made of bearing steel or the like. The tapered roller 4 has a small-diameter circular small-diameter end face 41 on one side in the roller axial direction (the left side in FIG. 1A, the right side in FIG. 1B), and the small diameter end surface 41 has a small diameter side end surface 41 on the other side in the roller axial direction (the right side in FIG. 1A, the right side in FIG. 1B). It has a circular large-diameter side end surface 42 with a large diameter on the left side). The tapered rollers 4 roll into contact with the inner ring raceway 21 and the outer ring raceway 31. The large-diameter side end surface 42 rolls into contact with the side surface (flange surface) 24 of the large flange portion 23 .

As shown in FIGS. 1 to 4, the cage 5 includes a small-diameter annular body 6 on one side in the axial direction, a large-diameter annular body 7 on the other side in the axial direction that has a larger outer diameter than the small-diameter annular body 6, and a large-diameter annular body 7 on the other side in the axial direction. It has a plurality of pillars 8 provided at intervals. The small-diameter annular body 6 and the large-diameter annular body 7 have an annular shape and are provided apart from each other in the axial direction. The pillar 8 connects the small diameter annular body 6 and the large diameter annular body 7. A pocket 9 is a space formed between the small-diameter annular body 6 and the large-diameter annular body 7 and between two circumferentially adjacent columns 8, 8. One tapered roller 4 is accommodated in each pocket 9.

The cage 5 has a plurality of pockets 9 for accommodating the tapered rollers 4, and holds the plurality of tapered rollers 4 at equal intervals in the circumferential direction.

The respective side surfaces 8a, 8a of the two pillars 8, 8 are opposed to each other inside the pocket 9. Each of the side surfaces 8a, 8a forms a predetermined angle such that the distance between the surfaces decreases toward the outside in the radial direction of the retainer 5. The side surface 8a has a role as a retaining portion that prevents the tapered roller 4 housed in the pocket 9 from falling off radially outward.

The small-diameter annular body 6 is formed with a small-diameter side surface 6a. The small-diameter side surface 6a is a portion facing the small-diameter side end surface 41 of the tapered roller 4 housed in the pocket 9. The small diameter side surface 6a has the role of restricting the small diameter side portion 4a of the tapered roller 4 housed in the pocket 9 from being displaced radially outward.

The large-diameter annular body 7 is formed with a large-diameter side surface 7a. The large-diameter side surface 7a is a portion facing the large-diameter end surface 42 of the tapered roller 4 housed in the pocket 9. The large-diameter side surface 7a has the role of restricting the large-diameter side portion 4b of the tapered roller 4 housed in the pocket 9 from being displaced radially outward.

Inside the pocket 9, a space is formed surrounded by the side surfaces 8a, 8a, the small diameter side surface 6a, and the large diameter side surface 7a. The tapered roller 4 accommodated in the pocket 9 has a conical outer circumferential surface 43 facing each side surface 8a, 8a. Further, the tapered roller 4 housed in the pocket 9 has a small diameter side end surface 41 facing the small diameter side surface 6a, and a large diameter side end surface 42 facing the large diameter side surface 7a.

The cage 5 has a groove 10 formed on the large diameter side surface 7a. The groove portion 10 has a role of retaining lubricating oil on the large-diameter side surface 7a. Note that the form of the groove portion 10 will be explained in detail later.

In the retainer 5, a recessed portion 8b is formed on each of the radially outer side surfaces of the pillars 8. In the pillar 8, the angle of inclination of the radially outer surface of the recessed portion 8b with respect to the center line C0 is smaller than the inclination angle of the radially outer surface of the pillar 8 with respect to the center line C0 of the portion other than the recessed portion 8b. In other words, in the recessed portion 8b, the inclination angle of the radially outer surface of the pillar 8 is closer to horizontal than in areas other than the recessed portion 8b. Therefore, lubricating oil is more likely to accumulate in the recess 8b than in areas other than the recess 8b. In the cage 5 having the recessed portions 8b, lubricating oil can be stored in a portion of the recessed portions 8b located above the oil pool when the tapered roller bearing 1 is not in operation. Further, in the retainer 5, by providing the recessed portion 8b, the lubricating oil attached to the radially outer side of the column 8 can easily flow toward the large diameter side surface 7a side. Therefore, in the cage 5 having the recessed portion 8b, the lubricating oil is held in the recessed portion 8b, and the lubricating oil is easily held in the groove portion 10 formed in the large diameter side surface 7a. The recessed portion 8b contributes to suppressing damage to the tapered roller bearing due to insufficient oil amount.

The cage 5 is made of synthetic resin and is molded by injection molding. The cage 5 of this embodiment is made of polyphenylene sulfide resin (PPS), for example. The cage 5 has resistance to lubricating oil (oil resistance), is relatively hard, and is difficult to elastically deform. The retainer 5 may be manufactured using a 3D printer.

In the present disclosure, the retainer 5 is capable of sliding contact with a part of the inner circumferential surface of the outer ring 3, so that the rotation of the retainer 5 is guided by the outer ring 3. That is, the tapered roller bearing 1 shown in FIG. 1 is an outer ring guided type bearing in which the retainer 5 is guided by the outer ring 3.

As explained above, in the tapered roller bearing 1 of the present disclosure, the cage 5 includes a small diameter annular body 6 provided on one side in the axial direction, a large diameter annular body 7 provided on the other side in the axial direction, and a small diameter annular body 7 provided on the other side in the axial direction. 6 and a large-diameter annular body 7, and a recessed portion 8b is provided on the outer side of the pillar 8 in the radial direction. According to this configuration, when the tapered roller bearing 1 is not in operation, lubricating oil can be stored in the recessed portion 8b located at a position that is not an oil reservoir. Moreover, according to the cage 5 having the recessed portion 8b, the lubricating oil can be made to flow easily from the pillar 8 toward the large-diameter side end surface 7a.

As shown in FIG. 1, the center line of the cage 5 is aligned with the center line of the inner ring 2, and a plurality of tapered rollers 4 held in the cage 5 are attached to the inner ring raceway 21 and the side surface of the large flange 23. (Flame surface) A state in which it is in proper contact with 24 is defined as a "reference state". In the reference state, where the tapered rollers 4 are in contact with the outer ring raceway 31, the tapered rollers 4 cannot be displaced in the roller radial direction and the roller axial direction. A gap is provided between the small diameter side end surface 41 of the tapered roller 4 and the small diameter annular body 6, and a gap is provided between the outer peripheral surface 43 of the tapered roller 4 and each side surface 8a of the column 8. It is being Therefore, the cage 5 can be slightly displaced relative to the tapered rollers 4 in the radial and axial directions.

In the standard state, an imaginary circle connecting the centers of the small-diameter end surface 41 of the tapered roller 4 is defined as the (designed) small-diameter pitch circle of the tapered roller 4, and a virtual circle connecting the centers of the large-diameter end surface 42 of the tapered roller 4 The connecting virtual circle is defined as the (designed) pitch circle on the larger diameter side of the tapered rollers 4.

[Groove according to the first embodiment]
FIG. 5 is a schematic configuration diagram showing the groove portion according to the first embodiment. The cage 5 constituting the tapered roller bearing 1 of the present disclosure can employ the groove portion 10 in the form shown in FIGS. 4 and 5. As shown in FIGS. 4 and 5, the groove portion 10 includes a plurality of V-shaped grooves 11. As shown in FIGS. The V-shaped groove 11 is a groove having a V-shape when viewed from a direction perpendicular to the large-diameter side surface 7a, and includes a first groove 11a, a second groove 11b, and a top 11c.

In each of the V-shaped grooves 11 constituting the groove portion 10, the first groove portion 11a is located on the radially outer side of the large diameter side surface 7a, and the second groove portion 11b is located on the radially inner side of the large diameter side surface 7a, Further, it is provided on the large-diameter side surface 7a with the top portion 11c facing one side in the circumferential direction of the large-diameter side surface 7a. In the groove portion 10, a plurality of V-shaped grooves 11 are formed side by side in the circumferential direction of the large-diameter side surface 7a, and have a herringbone shape. In addition, in the following description, the groove part 10 is also called "herringbone groove 10." In the following description, the herringbone groove 10 according to the first embodiment shown in FIGS. 4 and 5 is also referred to as a first herringbone groove 10A. Note that, although the first herringbone groove 10A shown in this embodiment includes five V-shaped grooves 11, the number of V-shaped grooves forming the herringbone groove of the present disclosure is not limited to this.

[About the flow of lubricating oil in the groove]
FIG. 6 is a schematic diagram showing the flow of lubricating oil in the groove according to the first embodiment. FIGS. 7A and 7B are partial cross-sectional views showing the positional relationship between the large-diameter end face of the tapered roller and the groove. In addition, in FIG. 6, for convenience of explanation, the intervals between the V-shaped grooves 11 are shown widened. FIG. 6 shows the flow of lubricating oil J around the herringbone groove 10 when the tapered roller 4 rotates in the direction of arrow R1 (see FIG. 7A). As shown in FIG. 6, when the tapered rollers 4 rotate in the direction of the arrow R1, the lubricating oil J flows into the first groove portion 11a and the second groove portion 11b as the tapered roller 4 rotates. As a result, the lubricating oil J is stored in the V-shaped groove 11. In the tapered roller bearing 1, lubricating oil J is retained in the V-shaped groove 11 when the bearing is in a non-operating state.

As the tapered roller 4 rotates in the direction of arrow R1, each lubricating oil J in the first groove 11a and the second groove 11b flows along each groove 11a, 11b, and near the top 11c. They merge and flow out to the outside of the V-shaped groove 11. The lubricating oil J flowing out from the V-shaped groove 11 located at the upper part of the tapered roller bearing 1 naturally flows down due to its own weight and reaches the side surface (flange surface) 24 of the large flange portion 23 located below the large diameter side surface 7a. reach. Thereby, the lubricating oil J can be supplied between the large diameter side end surface 42 and the side surface (flange surface) 24 of the tapered roller 4.

Furthermore, in the tapered roller bearing 1, dynamic pressure is generated between the groove portion 10 and the large-diameter side end surface 42 due to the flow of the lubricating oil J. In the tapered roller bearing 1, the tapered rollers 4 are displaced in the axial direction by the dynamic pressure, and a gap is created between the side surface (flange surface) 24 of the large flange portion 23 and the large diameter side end surface 42. Therefore, in the tapered roller bearing 1, the cage 5 can reliably supply lubricating oil to the gap created between the side surface (flange surface) 24 and the large diameter end surface 42. Thereby, damage to the tapered rollers 4 due to insufficient oil amount can be suppressed.

As shown in FIGS. 7A and 7B, in the cage 5, the first herringbone groove 10A is provided on the outside in the radial direction compared to the rotation center (the position of the central axis C1) of the large-diameter end surface 42 of the tapered roller 4. It is being In other words, in the tapered roller bearing 1 equipped with the cage 5, the pitch circles of the plurality of tapered rollers 4 are located on the inside of the groove portion 10 in the radial direction. In the tapered roller bearing 1 provided with the retainer 5, the range in which the large-diameter side end face 42 contacts the groove portion 10 is a range that is equal to or less than a semicircle of the large-diameter side end face 42 having a circular shape.

As shown in FIG. 7A, in the tapered roller bearing 1 used with the tapered rollers 4 rotating in the direction of arrow R1, the top portion 11c of each V-shaped groove 11 constituting the first herringbone groove 10A is It is preferable to orient it in a direction that coincides with the rotational direction of the rollers 4 (the direction of arrow R1). As shown in FIG. 7B, in the tapered roller bearing 1 used with the tapered rollers 4 rotating in the direction of arrow R2, the top portion 11c of each V-shaped groove 11 constituting the first herringbone groove 10A is It is preferable to orient it in a direction that coincides with the rotational direction of the rollers 4 (direction of arrow R2). In the tapered roller bearing 1 having such a configuration, by aligning the direction of the herringbone grooves 10 with the rotating direction of the tapered rollers 4, a gap can be created between the side surface (flange surface) 24 and the large diameter end surface 42. Dynamic pressure can be reliably generated.

As described above, the tapered roller bearing 1 of the present disclosure includes, on the outer circumferential side, an inner ring raceway 21, a small flange portion 22 provided on one side in the axial direction of the inner ring raceway 21, and an axis of the inner ring raceway 21. An inner ring 2 having a large flange 23 provided on the other side in the direction, an outer ring 3 having an outer ring raceway 31 on the inner circumferential side, a plurality of tapered rollers 4 that roll into contact with the inner ring raceway 21 and the outer ring raceway 31, An annular retainer 5 having a plurality of pockets 9 for accommodating rollers 4 is provided. Each of the plurality of pockets 9 has a small diameter side surface 6a opposite to the small diameter end surface 41 of the tapered roller 4 to be accommodated, a large diameter side surface 7a opposite to the large diameter side end surface 42 of the tapered roller 4 to be accommodated, and a large diameter side surface 7a to the large diameter side end surface 42 of the tapered roller 4 to be accommodated. It has a groove 10 formed in the side surface 7a. In the tapered roller bearing 1, the groove portion 10 includes a plurality of V-shaped grooves 11 having a V-shaped form when viewed from a direction perpendicular to the large-diameter side surface 7a, and the top portion 11c of the V-shaped groove 11 has a large diameter. This is a herringbone groove 10 in which a plurality of V-shaped grooves 11 are arranged side by side in the circumferential direction of the large-diameter side surface 7a while facing in the circumferential direction of the side surface 7a. According to such a tapered roller bearing 1, the lubricating oil J can be stored in the large diameter side surface 7a of the cage 5 by the groove portion 10 configured as a herringbone groove, and when the tapered roller bearing 1 is not in operation, the lubricating oil J can be stored. , it becomes possible to hold lubricating oil on the large-diameter side surface 7a. In this case, immediately after the tapered roller bearing 1 starts operating, it becomes possible to supply the lubricating oil J held on the large-diameter side surface 7a to the tapered rollers 4 and the inner ring 2. Damage can be suppressed.

[Groove according to second embodiment]
FIG. 8 is a schematic configuration diagram showing a groove portion according to the second embodiment. In the retainer 5 constituting the tapered roller bearing 1 of the present disclosure, the herringbone groove 10 may have the form shown in FIG. 8 . In the following description, the herringbone groove 10 according to the second embodiment shown in FIG. 8 is also referred to as a second herringbone groove 10B.

The second herringbone groove 10B is composed of a plurality of V-shaped grooves 11. The V-shaped groove 11 constituting the second herringbone groove 10B includes a first V-shaped groove 11A, which is the first V-shaped groove 11, and a second V-shaped groove, which is the second V-shaped groove 11. 11B is included. The first V-shaped groove 11A includes a first groove portion 11a, a second groove portion 11b, and a top portion 11c. The second V-shaped groove 11B includes a first groove portion 11d, a second groove portion 11b, and a top portion 11e.

In the second herringbone groove 10B, the radially outer half of the second groove portion 11b constitutes the first V-shaped groove 11A, and the radially inner half of the second groove portion 11b constitutes the first V-shaped groove 11A. The first V-shaped groove 11A and the second V-shaped groove 11B share the second groove portion 11b. Therefore, in the second herringbone groove 10B, one first V-shaped groove 11A and one second V-shaped groove 11B are integrated, and the whole has a substantially S-shaped form. Note that in the second herringbone groove 10B of this embodiment, the first V-shaped groove 11A and the second V-shaped groove 11B are integrated, but the first V-shaped groove 11A and the second V-shaped groove 11B are separated. You may do so.

In the second herringbone groove 10B, the first V-shaped groove 11A has an apex 11c facing the first circumferential direction (approximately to the left in FIG. 8) of the large-diameter side surface 7a, and a diameter of the large-diameter side surface 7a. The second V-shaped groove 11B has a top portion 11e facing in the second direction (approximately to the right in FIG. 8) in the circumferential direction of the large-diameter side surface 7a, and is located on the outside of the first V-shaped groove 11A. and is arranged radially inside the large-diameter side surface 7a.

In the cage 5 having the second herringbone grooves 10B, when the rotation direction of the tapered rollers 4 is in the arrow R1 (see FIG. 7A), each of the first V-shaped grooves 11A plays a role of generating dynamic pressure. , when the rotational direction of the tapered roller 4 is arrow R2 (see FIG. 7B), each second V-shaped groove 11B plays the role of generating dynamic pressure. Therefore, in the tapered roller bearing 1 using the cage 5 having the second herringbone groove 10B, the rotation direction of the tapered rollers 4 is either arrow R1 (see FIG. 7A) or arrow R2 (see FIG. 7B). Also, dynamic pressure can be generated by the lubricating oil J (see FIG. 6) existing in the groove portion 10. Therefore, the cage 5 having the second herringbone groove 10B can be used regardless of the rotation direction of the tapered rollers 4.

As described above, the second herringbone groove 10B constituting the tapered roller bearing 1 of the present disclosure has the top portion 10c facing the first direction in the circumferential direction of the large diameter side surface 7a, and The first V-shaped groove 11A is arranged on the outside in the radial direction, and the top part 10e faces the second direction in the circumferential direction of the large-diameter side surface 7a, and the first V-shaped groove 11A is arranged on the inside in the radial direction of the large-diameter side surface 7a. The second V-shaped groove 11B includes a second V-shaped groove 11B. According to this configuration, it is possible to supply lubricating oil to the tapered rollers 4 from the groove portion 10 (second herringbone groove 10B) regardless of the rotation direction of the tapered rollers 4.

[Groove according to third embodiment]
FIG. 9 is a schematic configuration diagram showing a groove portion according to the third embodiment. In the retainer 5 constituting the tapered roller bearing 1 of the present disclosure, the herringbone groove 10 may have the form shown in FIG. 9 . In the following description, the herringbone groove 10 according to the third embodiment shown in FIG. 9 is also referred to as a third herringbone groove 10C. The third herringbone groove 10C differs from the second herringbone groove 10B in that the width of the region in which the V-shaped groove 11 is formed in the radial direction differs between the radially outer side and the radially inner side.

The third herringbone groove 10C is composed of a plurality of V-shaped grooves 11. The V-shaped groove 11 constituting the third herringbone groove 10C includes a third V-shaped groove 11C, which is the third V-shaped groove 11, and a fourth V-shaped groove, which is the fourth V-shaped groove 11. 11D is included. The third V-shaped groove 11C includes a first groove portion 11a, a second groove portion 11b, and a top portion 11c. The fourth V-shaped groove 11D includes a first groove portion 11d, a second groove portion 11b, and a top portion 11e.

In the third herringbone groove 10C, a part of the radially outer side of the second groove part 11b (a part included in the width W3 of the formation area described later) constitutes the third V-shaped groove 11C, and the diameter of the second groove part 11b is A part of the inner side in the direction (a part included in the width W4 of the formation area described later) constitutes the fourth V-shaped groove 11D, and the third V-shaped groove 11C and the fourth V-shaped groove 11D form the second groove part 11b. are shared. The third herringbone groove 10C shares the second groove portion 11b of the third V-shaped groove 11C and the second groove portion 11b of the fourth V-shaped groove 11D. Therefore, in the third herringbone groove 10C, one third V-shaped groove 11C and one fourth V-shaped groove 11D are integrated, and the whole has a substantially S-shaped form. In addition, in the third herringbone groove 10C of this embodiment, the third V-shaped groove 11C and the fourth V-shaped groove 11D are integrated, but the third V-shaped groove 11C and the fourth V-shaped groove 11D are separated. You may do so.

In the third herringbone groove 10C, the third V-shaped groove 11C has an apex 11c facing the first circumferential direction (approximately to the left in FIG. 9) of the large-diameter side surface 7a, and a diameter of the large-diameter side surface 7a. The fourth V-shaped groove 11D is arranged so that the top portion 11e thereof faces in the second direction (approximately to the right in FIG. 9) in the circumferential direction of the large-diameter side surface 7a, and the fourth V-shaped groove 11D is arranged on the outside of the third V-shaped groove 11C. and is arranged radially inside the large-diameter side surface 7a.

In the third herringbone groove 10C, the width W3 of the formation region of the third V-shaped groove 11C is smaller than the width W4 of the formation region of the fourth V-shaped groove 11D in the radial direction of the large-diameter side surface 7a.

In the cage 5 having the third herringbone grooves 10C, when the rotation direction of the tapered rollers 4 is in the arrow R1 (see FIG. 7A), each third V-shaped groove 11C plays a role of generating dynamic pressure. , when the rotation direction of the tapered roller 4 is arrow R2 (see FIG. 7B), each fourth V-shaped groove 11D plays a role of generating dynamic pressure.

The magnitude of the dynamic pressure generated by the lubricating oil J (see FIG. 6) existing in the groove 10 has a correlation with the moving speed of the large-diameter side end face 42 facing the groove 10, and when the moving speed is large, the dynamic pressure is generated. The dynamic pressure increases. The circumferential speed of the large-diameter side end surface 42 increases toward the outer side in the radial direction, and decreases toward the inner side in the radial direction. Therefore, in the second herringbone groove 10B (see FIG. 8) described above, the dynamic pressure generated from the first V-shaped groove 11A located on the radially outer side of the groove portion 10 and the second V-shaped groove located on the radially inner side of the groove portion 10 are combined. There is a possibility that a difference will occur between the dynamic pressure generated from the character-shaped groove 11B.

In the third herringbone groove 10C, the width W3 of the formation region of the third V-shaped groove 11C is smaller than the width W4 of the formation region of the fourth V-shaped groove 11D. That is, in the third herringbone groove 10C, the third V-shaped groove 11C located on the outside in the radial direction where the circumferential speed of the large-diameter side end surface 42 is large is made smaller in width W3 of the formation region, and The fourth V-shaped groove 11D, which is located on the radially inner side where the circumferential speed of the groove 11D becomes smaller, has a smaller width W4 of its formation region.

In the cage 5 having such a third herringbone groove 10C, the difference between the dynamic pressure generated from the third V-shaped groove 11C on the radially outer side and the dynamic pressure generated from the fourth V-shaped groove 11D on the radially inner side is suppressed. Can be suppressed. In the cage 5 having the third herringbone groove 10C, the dynamic pressure when the rotation direction of the tapered rollers 4 is arrow R1 (see FIG. 7A) and the dynamic pressure when the rotation direction is arrow R2 (see FIG. 7B) The pressure can be a similar dynamic pressure. Therefore, in the cage 5 having the third herringbone groove 10C, the rotation direction of the tapered rollers 4 is indicated by the arrow R2 (see FIG. 7B), and each of the fourth V-shaped grooves 11D plays the role of generating dynamic pressure. In some cases, it is possible to prevent insufficient dynamic pressure from occurring.

In other words, in the cage 5 having the third herringbone groove 10C, regardless of whether the tapered roller 4 rotates in the direction of arrow R1 (see FIG. 7A) or arrow R2 (see FIG. 7B), 24 and the large-diameter side end surface 42, and the lubricating oil J can be supplied to the gap. According to the cage 5 having the third herringbone groove 10C, damage to the tapered rollers 4 due to insufficient oil amount can be more reliably suppressed, and the tapered rollers 4 can be used without worrying about the rotating direction. becomes possible. In addition, in the first herringbone groove 10A (see FIG. 5), the groove lengths of the first groove part 11a and the second groove part 11b are approximately the same, but the first groove part 11a in the first herringbone groove 10A The groove lengths of the second groove portion 11b may also be different. In this case, it is preferable that the groove length of the first groove part 11a is shorter than the groove length of the second groove part 11b.

As explained above, the third herringbone groove 10C constituting the tapered roller bearing of the present disclosure includes the first V-shaped groove 11C located on the radially outer side of the large-diameter side surface 7a and the first V-shaped groove 11C located on the radially outer side of the large-diameter side surface 7a. In the radial direction of the large-diameter side surface 7a, the width W3 of the formation area of the first V-shaped groove 11C is equal to the width W4 of the formation area of the second V-shaped groove 11D. small compared to According to this configuration, the dynamic pressure generated when the rotation direction of the tapered roller 4 is the first direction (for example, the direction of arrow R1 shown in FIG. 7A), and the dynamic pressure that occurs when the rotation direction of the tapered roller 4 is the second direction (for example, 7B), it is possible to make the dynamic pressure generated to the same extent.

In the above disclosure, a single-row tapered roller bearing 1 in which a plurality of tapered rollers 4 are lined up in a row in the circumferential direction has been described. Although not shown, the cage of the double-row tapered roller bearing may have the above configuration. In addition, as another form, when a part of a wheel bearing device (also called a hub unit) that supports the wheels of an automobile is constituted by a tapered roller bearing, in other words, the wheel bearing device is one part. When the part has tapered rollers as rolling elements, the cage that holds the tapered rollers may have the above-mentioned configuration.

The form disclosed this time is illustrative in all respects and is not restrictive. The scope of the present invention is not limited to the above-mentioned form, but includes all changes within the scope of equivalents to the configuration described in the claims.

1: Tapered roller bearing 2: Inner ring 3: Outer ring 4: Tapered roller 5: Cage 6: Small diameter annular body 6a: Small diameter side side 7: Large diameter annular body 7a: Large diameter side side 8: Pillar 8b: Recessed part 9: Pocket 10: Groove (herringbone groove)
11: V-shaped groove 11A: First V-shaped groove (first V-shaped groove)
11B: Second V-shaped groove (second V-shaped groove)
11C: First V-shaped groove (first V-shaped groove)
11D: Second V-shaped groove (second V-shaped groove)
11a: First groove 11d: First groove 11b: Second groove 11c: Top 11e: Top 21: Inner raceway 22: Small flange 23: Large flange 31: Outer raceway 41: Small diameter end face 42: Large diameter end face

Claims (4)

an inner ring having an inner ring raceway, a small flange part provided on one axial side of the inner ring raceway, and a large flange part provided on the other axial side of the inner ring raceway on the outer circumferential side;
an outer ring having an outer ring raceway on the inner circumferential side;
a plurality of tapered rollers that roll into contact with the inner raceway and the outer raceway;
an annular retainer having a plurality of pockets for accommodating the tapered rollers;
Each of the plurality of pockets has a small-diameter side surface facing the small-diameter end surface of the tapered roller to be accommodated, and a large-diameter side surface facing the large-diameter side end surface of the tapered roller to be accommodated;
a groove formed on the large-diameter side surface;
The groove portion is
The large diameter side surface includes a plurality of V-shaped grooves each having a V-shaped configuration when viewed from a direction perpendicular to the large diameter side surface, and the top part of the V shaped groove is directed in the circumferential direction of the large diameter side surface. A tapered roller bearing that is a herringbone groove in which a plurality of the V-shaped grooves are arranged in a circumferential direction on a radial side surface. The herringbone groove is
the first V-shaped groove, the top of which faces in a first direction in the circumferential direction of the large-diameter side surface and is disposed on the outside of the large-diameter side surface in the radial direction;
1 . The second V-shaped groove, the top of which faces in a second direction in the circumferential direction of the large-diameter side surface and is disposed radially inside the large-diameter side surface. Tapered roller bearings described in . The herringbone groove is
the first V-shaped groove located on the radially outer side of the large-diameter side surface; and the second V-shaped groove located on the radially inner side of the large-diameter side surface;
According to claim 1 or claim 2, in the radial direction of the large-diameter side surface, the width of the region where the first V-shaped groove is formed is smaller than the width of the region where the second V-shaped groove is formed. Tapered roller bearings listed. The retainer includes a small diameter annular body provided on one axial side, a large diameter annular body provided on the other axial side, and a plurality of columns connecting the small diameter annular body and the large diameter annular body. death,
The tapered roller bearing according to claim 1 or 2, wherein a recessed portion is provided on the radially outer side of the pillar.

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