Tapered roller bearing

Abstract

A tapered roller bearing (10) has an outer ring (11), an inner ring (12), a plurality of tapered rollers (13), and a ring-shaped retainer (14). The retainer (14) has a small-diameter annular portion (15), a large-diameter annular portion (16), and a plurality of columns (17) connecting the small-diameter annular portion (15) and the large-diameter annular portion (16). The inner ring (12) has a large flange portion (24) in sliding contact with a large end surface (38). A recess (20) is provided in the large-diameter annular portion (16) and opens toward the large end surface (38). A first gap between the large-diameter annular portion (16) and the outer ring (11) is smaller than a second gap between the small-diameter annular portion (15) and the outer ring (11). The large-diameter annular portion (16) has a tapered surface (31) in the outer periphery that expands in diameter toward the other side in the axial direction. The tapered surface (31) has a facing portion located on the side of the axial direction relative to an imaginary plane of a side surface (81) on the other side in the axial direction of the outer ring (11) and facing the inner peripheral surface of the outer ring (11).

Description

Technical Field

[0001] This disclosure relates to tapered roller bearings. Background Technology

[0002] A tapered roller bearing comprises an outer ring, an inner ring, a plurality of tapered rollers, and an annular cage holding the tapered rollers. Each tapered roller has a small end face on one axial side and a large end face on the other axial side. The inner ring has a large flange portion that slides in contact with the large end face of the tapered roller (see, for example, Patent Document 1).

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2018-3942 Summary of the Invention

[0006] The problem that the invention aims to solve

[0007] In tapered roller bearings, when the inner ring rotates, the large end face of the tapered roller makes sliding contact with the large flange of the inner ring. During rotational start-up, if there is insufficient lubricating oil between the tapered roller and the large flange, or even if the lubricating oil supplied during rotation is insufficient and the bearing is in a state of poor lubrication, sintering can easily occur between the tapered roller and the large flange.

[0008] In the tapered roller bearing disclosed in Patent Document 1, the clearances between the outer ring and the inner ring and the major diameter annular portion of the cage are small. Therefore, the lubricating oil inside the bearing containing the tapered rollers is difficult to flow out of the bearing, and the lubricating oil can be used to prevent sintering between the tapered rollers and the large flange portion.

[0009] Therefore, in tapered roller bearings, it is necessary to prevent sintering between the tapered rollers and the large flange of the inner ring, and it is hoped that new technical means can be developed to improve the function of preventing sintering.

[0010] Methods for solving problems

[0011] The tapered roller bearing disclosed herein comprises: an outer ring having an outer ring raceway surface that expands in diameter from one axial side toward the other; an inner ring having an inner ring raceway surface that expands in diameter from one axial side toward the other; a plurality of tapered rollers having a large end face on the other axial side; and an annular cage holding the plurality of tapered rollers, the cage having: a small-diameter annular portion located on one axial side of the tapered rollers; a large-diameter annular portion located on the other axial side of the tapered rollers; and a plurality of columns connecting the small-diameter annular portion and the large-diameter annular portion. The ring portion has a large flange portion that slides in contact with the large end face. The large diameter annular portion has a recess that opens toward the large end face. The first gap is smaller than the second gap. The first gap is the gap between the large diameter annular portion and the outer ring. The second gap is the gap between the small diameter annular portion and the outer ring. The large diameter annular portion has an inclined surface on its outer periphery. The inclined surface expands in diameter toward the other side of the axial direction. The inclined surface has a facing surface that is located on the axial side of the imaginary plane of the side surface along the other side of the axial direction of the outer ring and is opposite to the inner circumferential surface of the outer ring.

[0012] Invention Effects

[0013] According to the tapered roller bearing disclosed herein, the function of preventing sintering between the large flange portion of the inner ring and the large end face of the tapered roller can be improved. Attached Figure Description

[0014] Figure 1 This is a cross-sectional view showing an example of a tapered roller bearing.

[0015] Figure 2 It is an enlarged sectional view showing the large-diameter annulus of the cage and its surrounding area.

[0016] Figure 3 It is a cross-sectional view of the face passing through the column of the cage.

[0017] Figure 4 This is an explanatory diagram showing the cage and tapered rollers viewed radially outward from the column as the center.

[0018] Figure 5 It is an enlarged sectional view showing the small-diameter annulus and its surrounding area, and the large-diameter annulus and its surrounding area. Detailed Implementation

[0019] <Summary of Embodiments of the Invention Disclosed>

[0020] The following is a summary description of embodiments of the invention disclosed herein.

[0021] (1) The tapered roller bearing of this disclosure comprises: an outer ring having an outer ring raceway surface that expands in diameter from one axial side to the other axial side; an inner ring having an inner ring raceway surface that expands in diameter from one axial side to the other axial side; a plurality of tapered rollers having a large end face on the other axial side; and an annular cage holding the plurality of tapered rollers, the cage having: a small-diameter annular portion located on one axial side of the tapered rollers; a large-diameter annular portion located on the other axial side of the tapered rollers; and a plurality of columns connecting the small-diameter annular portion and the large-diameter annular portion, wherein... The inner ring has a large flange portion that slides in contact with the large end face. The large-diameter annular portion has a recess that opens toward the large end face. The first gap is smaller than the second gap. The first gap is the gap between the large-diameter annular portion and the outer ring. The second gap is the gap between the small-diameter annular portion and the outer ring. The large-diameter annular portion has an inclined surface on its outer periphery. The inclined surface expands in diameter toward the other side of the axial direction. The inclined surface has a facing surface portion. The facing surface portion is located on the axial side of the imaginary plane of the side surface along the other side of the axial direction of the outer ring and is opposite to the inner circumferential surface of the outer ring.

[0022] According to the tapered roller bearing, the first clearance between the outer ring and the major diameter annular portion of the cage is small. The major diameter annular portion, like the raceway surface of the outer ring, has an inclined surface that expands in diameter towards the opposite axial direction, and this inclined surface has a facing portion opposite to the outer ring. Therefore, lubricating oil is difficult to flow out between the inner circumferential surface of the outer ring and the facing portion of the major diameter annular portion.

[0023] Furthermore, lubricating oil accumulates in the recess of the large-diameter annulus. Because the first gap is small, the outer circumferential surface of the large-diameter annulus is close to the outer ring. Therefore, the large-diameter annulus increases radially, thereby expanding the volume of the recess.

[0024] This makes it easier to supply lubricating oil from the other side of the axial direction to the large flange of the inner ring and the large end face of the tapered roller, thereby improving the function of preventing sintering between them.

[0025] (2) When the tapered roller bearing rotates, the lubricating oil flows from one axial side to the other axial side. Therefore, it is preferable that, in the tapered roller bearing, when the gap between the outer circumferential surface of the large diameter annulus portion and the large flange portion is set as the third gap, and the gap between the small diameter annulus portion and the inner ring is set as the fourth gap, the sum of the first gap and the third gap is greater than the sum of the second gap and the fourth gap.

[0026] As described above, the first gap is smaller than the second gap, but according to the above structure, the combined gap of the third gap and the first gap is larger than the combined gap of the fourth gap and the second gap. That is, the gap on the downstream side of the lubricating oil flow direction is larger than the gap on the upstream side. Therefore, when the bearing is rotating, the lubricating oil is less likely to remain inside the bearing, which reduces the stirring resistance of the rotating cage to the lubricating oil.

[0027] (3) Preferably, the column has an outer surface on the radially outer side, the outer surface causing the distance between the outer surface and the inner circumferential surface of the outer ring to increase as it moves toward the other side of the axial direction.

[0028] In this case, with the centerline of the tapered roller bearing horizontal, when the bearing is stopped, the space for lubricating oil to accumulate between the shaft and the outer ring can be expanded on the bottom side of the tapered roller bearing. When the bearing starts to rotate, the lubricating oil in this space can be used for lubrication.

[0029] (4) In the tapered roller bearing of (3), it is further preferred that the column has a wall extending from the end of the outer side on the other side of the axial direction toward the outer ring side, the wall being positioned on the axial side of the larger diameter annulus portion.

[0030] In this case, as the bearing rotates, the lubricating oil flowing axially to the other side along the outer side of the cage encounters the wall surface. As a result, the flow direction of the lubricating oil changes to circumferential, facilitating the supply of lubricating oil to the pockets holding the tapered rollers and to the large end face side of the tapered rollers.

[0031] <Details of the embodiments of the present invention>

[0032] The embodiments of the invention disclosed herein will be described below.

[0033] [Regarding the overall structure of tapered roller bearings]

[0034] Figure 1 This is a cross-sectional view showing an example of a tapered roller bearing. The tapered roller bearing 10 includes an outer ring 11, an inner ring 12, a plurality of tapered rollers 13, and an annular cage 14. The centerline of the outer ring 11 coincides with the centerline of the inner ring 12, and these centerlines are called the centerline L of the tapered roller bearing 10. In this embodiment, the inner ring 12 is a rotating ring that rotates with a shaft (not shown), and the outer ring 11 is a fixed ring mounted on a housing (not shown), but the outer ring 11 may also be a rotating ring.

[0035] The direction along the centerline L and the direction parallel to the centerline L are defined as the "axial direction" of the tapered roller bearing 10. Figure 1 The left side of the image is the "axial side". Figure 1The right side of the axis is defined as "the other side of the axis". The direction orthogonal to the center line L is defined as the "radial" direction of the tapered roller bearing 10. The direction along the circle centered on the center line L is defined as the "circumferential" direction of the tapered roller bearing 10.

[0036] The tapered roller bearing 10 maintains its lubrication performance through lubricating oil. When the tapered roller bearing 10 rotates, the lubricating oil inside the bearing, between the outer ring 11 and the inner ring 12 and containing the tapered rollers 13, flows from one axial side to the other. Through this action, lubricating oil existing on the axial side of the bearing exterior of the tapered roller bearing 10 penetrates into the bearing interior, passes through the bearing interior, and flows to the bearing exterior on the other axial side. The tapered roller bearing 10 is lubricated by this lubricating oil.

[0037] The tapered roller 13 has a small end face 37 on one side of its axial direction and a large end face 38 on the other side of its axial direction.

[0038] The outer ring 11 is cylindrical and has an outer ring raceway surface 21 on its inner circumferential surface. The outer ring raceway surface 21 expands in diameter from one axial side to the other axial side.

[0039] The inner ring 12 is cylindrical and has an inner ring raceway surface 27 on its outer circumferential surface. The inner ring raceway surface 27 increases in diameter from one axial side to the other axial side. The inner ring 12 has a small flange portion 22 on one axial side and a large flange portion 24 on the other axial side. The small flange portion 22 protrudes radially outward from the inner ring raceway surface 27. The large flange portion 24 protrudes radially outward from the inner ring raceway surface 27. The outer circumferential surface 25 of the large flange portion 24 is larger radially than the outer circumferential surface 23 of the small flange portion 22. The large flange portion 24 has a flange surface 26 that makes sliding contact with the large end face 38 of the tapered roller 13.

[0040] The cage 14 has a small-diameter annular portion 15 located on one axial side of the tapered roller 13, a large-diameter annular portion 16 located on the other axial side of the tapered roller 13, and a plurality of posts 17 connecting the small-diameter annular portion 15 and the large-diameter annular portion 16. The area between the small-diameter annular portion 15 and the large-diameter annular portion 16 and between two adjacent posts 17, 17 in the circumferential direction forms a pocket 18 for holding one tapered roller 13.

[0041] A first recess 19 is provided in the small-diameter annular portion 15, opening toward the small end face 37 of the tapered roller 13. A second recess 20 is provided in the large-diameter annular portion 16, opening toward the large end face 38 of the tapered roller 13. The post 17 extends from the radially outer portion 15a of the small-diameter annular portion 15. The radially inner portion 15b of the small-diameter annular portion 15 extends radially from the radially outer portion 15a and is not connected to the post 17. Therefore, the radially inner portion 15b is more easily deformed. The post 17 is connected to both the radially outer portion 16a and the radially inner portion 16b of the large-diameter annular portion 16.

[0042] From Figure 1 The assembly state shown with the outer ring 11 removed is considered the disassembled state. In the disassembled state, the pocket 18 of the cage 14 prevents the tapered roller 13 from falling out radially outward and retains the tapered roller 13. Therefore, the column 17 has a contact portion 28 that contacts the tapered roller 13 from the radially outward (see reference). Figure 4 ). Figure 4 This is an explanatory diagram showing the cage 14 and tapered roller 13 viewed radially outward from the center of column 17. The contact portion 28 is provided in such a way that it protrudes circumferentially from the main body 17a of column 17 to both sides.

[0043] like Figure 1 As shown, the state in which the centerline of the cage 14 is aligned with the centerline L of the tapered roller bearing 10 is defined as the "reference state". The reference state is the state in which the small end face 37 of the tapered roller 13 contacts the small diameter annular portion 15 of the cage 14. In the reference state, the contact portion 28 between the tapered roller 13, which contacts the inner ring raceway surface 27, and the cage 14 has a slight gap in the radial direction. Within this gap, the cage 14 can be displaced in the radial direction.

[0044] The cage 14 has a guide surface 29 on a portion of its outer peripheral surface that can contact the inner peripheral surface of the outer ring 11. The guide surface 29 contacts the inner peripheral surface of the outer ring 11 (outer ring raceway surface 21), thereby positioning the cage 14 radially. That is, the cage 14 of this embodiment is an outer ring-guided cage. A portion of the large-diameter annular portion 16 (the opposing portion 32 described later, see reference 1) Figure 2 ) and a portion of column 17 connected to that portion (extension surface 35, described later, see reference) Figure 2 ) becomes the guiding surface 29.

[0045] Figure 2 This is an enlarged cross-sectional view showing the large-diameter annular portion 16 of the cage 14 and its surrounding area. Figure 2 The sectional view shown is containing Figure 1 A cross-sectional view of the centerline L shown. Figure 2 In the middle, the shaded part of the cage 14 is the large-diameter annular part 16.

[0046] The large-diameter annular portion 16 has an inclined surface 31 and an outer cylindrical surface 34 on its outer periphery. The inclined surface 31 is a surface that expands in diameter towards the opposite axial direction. The inclined surface 31 has a facing surface 32 that faces the inner circumferential surface 11a of the outer ring 11 and a non-facing surface 33 that does not face the inner circumferential surface 11a of the outer ring 11. The facing surface 32 is located axially closer to the imaginary plane K1 on the side surface 81 along the opposite axial direction of the outer ring 11, and faces the inner circumferential surface 11a of the outer ring 11. The non-facing surface 33 is located axially closer to the imaginary plane K1, and does not face the inner circumferential surface 11a of the outer ring 11. The facing surface 32 and the non-facing surface 33 are continuously arranged on the outer periphery of the large-diameter annular portion 16. Figure 2 In the cross section shown, a non-opposite face 33 is provided along the extension line of the opposite face 32.

[0047] The outer cylinder surface 34 will be described. The outer cylinder surface 34 is a surface that is continuous with the non-opposing surface 33 via the bend 36. The outer cylinder surface 34 is centered on the centerline L (refer to...). Figure 1 The surface with an inclination angle smaller than that of inclined surface 31, or along the centerline L (refer to) Figure 1 The outer cylindrical surface 34 is a hypothetical cylindrical surface based on the inclined surface 31. Like the inclined surface 31, the outer cylindrical surface 34 is a continuous surface in the circumferential direction.

[0048] Column 17 has an extended surface 35 on the opposite side of the axial direction, continuous with the inclined surface 31. (Referring to the centerline L) Figure 1 The tilt angle based on the reference is the same on the extended surface 35 and the tilted surface 31. The tilted surface 31 is a continuous surface in the circumferential direction, while the extended surface 35 is partially provided on both sides of the column 17 in the circumferential direction and is a discontinuous surface in the circumferential direction. The opposing surface 32 and the extended surface 35 form a guide surface 29 that can contact the outer ring 11.

[0049] Figure 3 This is a cross-sectional view of the centerline L and the surface of the retainer 14 passing through the column 17. The column 17 has a first outer surface 41 and a second outer surface 42 on its radially outer side. The first outer surface 41 has a shape along a first imaginary conical surface, which is a surface that widens the gap E1 between the first outer surface 41 and the inner circumferential surface 11a of the outer ring 11 as it moves toward the other side of the axial direction, and the first imaginary conical surface narrows as it moves toward one side of the axial direction. The first outer surface 41 is located on the axial side closer than the inclined surface 31 and the extended surface 35.

[0050] The second outer surface 42 has a shape along a second imaginary conical surface, which tapers in diameter towards the axial direction. With the centerline L as a reference, the inclination angle of the second outer surface 42 is the same as the inclination angle of the inner circumferential surface 11a (outer ring raceway surface 21) of the outer ring 11. That is, the second outer surface 42 is a surface with a constant spacing E2 between it and the inner circumferential surface 11a of the outer ring 11. The first outer surface 41 and the second outer surface 42 are continuous via a bend 43. The second outer surface 42 is continuous with the outer circumferential surface 15c of the small-diameter annular portion 15. The inclination angle of the second outer surface 42 is the same as the inclination angle of the outer circumferential surface 15c of the small-diameter annular portion 15.

[0051] The column 17 has a wall surface 44 extending from an end 41a on the other side of the first outer surface 41 toward the outer ring 11. For example... Figure 3 and Figure 4 As shown, the wall surface 44 is located on the axial side of the larger diameter annular portion 16. The wall surface 44 is a surface facing the axial side. The wall surface 44 is continuous with the extended surface 35 via the bend 45.

[0052] Figure 5 This is an enlarged cross-sectional view showing the small-diameter annular portion 15 and its surroundings, and the large-diameter annular portion 16 and its surroundings of the cage 14. The gap formed in the reference state between the large-diameter annular portion 16 and the end 61 on the other side of the axial direction of the outer ring 11 is designated as "first gap 51". The gap formed in the reference state between the small-diameter annular portion 15 and the end 62 on one side of the axial direction of the outer ring 11 is designated as "second gap 52". The gap formed in the reference state between the large-diameter annular portion 16 and the large flange portion 24 of the inner ring 12 is designated as "third gap 53". The gap formed in the reference state between the small-diameter annular portion 15 and the small flange portion 22 of the inner ring 12 is designated as "fourth gap 54".

[0053] The radial dimension of the first gap 51 is "R1", the radial dimension of the second gap 52 is "R2", the radial dimension of the third gap 53 is "R3", and the radial dimension of the fourth gap 54 is "R4". Furthermore, the dimensions R1, R2, R3, and R4 are the dimensions of the smallest radial portion of each gap.

[0054] The first gap 51 is smaller than the second gap 52. That is, the radial dimension R1 of the first gap 51 is smaller than the radial dimension R2 of the second gap 52 (R1 < R2). Figure 2 In the cross-section shown, under the reference state, the inner circumferential surface 11a of the outer ring 11 is parallel to the inclined surface 31 of the large diameter ring portion 16, and there is a first gap 51 between the inner circumferential surface 11a and the inclined surface 31, the radial dimension of which is R1.

[0055] exist Figure 5In this structure, the first gap 51 and the second gap 52 are continuously formed in the circumferential direction. Therefore, the first gap 51 forms a first annular gap 56 between the large-diameter annular portion 16 and the end 61 of the outer ring 11. The second gap 52 forms a second annular gap 57 between the small-diameter annular portion 15 and the end 62 of the outer ring 11. The first annular gap 56 has an annular shape that is larger in the radial direction than the second annular gap 57, but the opening area of ​​the first annular gap 56 is smaller than the opening area of ​​the second annular gap 57.

[0056] The sum of the first gap 51 and the third gap 53 is greater than the sum of the second gap 52 and the fourth gap 54. That is, the sum of the radial dimension R1 of the first gap 51 and the radial dimension R3 of the third gap 53 is greater than the sum of the radial dimension R2 of the second gap 52 and the radial dimension R4 of the fourth gap 54 (R1+R3>R2+R4).

[0057] The third gap 53 and the fourth gap 54 are formed continuously in the circumferential direction. Therefore, through the third gap 53, a third annular gap 58 is formed between the large flange portion 24 and the large diameter annular portion 16 of the inner ring 12. Through the fourth gap 54, a fourth annular gap 59 is formed between the small flange portion 22 and the small diameter annular portion 15 of the inner ring 12. The sum of the opening area A1 of the first annular gap 56 and the opening area A3 of the third annular gap 58 is greater than the sum of the opening area A2 of the second annular gap 57 and the opening area A4 of the fourth annular gap 59 (A1+A3>A2+A4).

[0058] [Regarding the tapered roller bearing 10 in this embodiment]

[0059] As described above, this embodiment (refer to...) Figure 1 The tapered roller bearing 10 includes an outer ring 11, an inner ring 12, a plurality of tapered rollers 13, and an annular cage 14 holding the plurality of tapered rollers 13. The cage 14 has a small-diameter annular portion 15 located on one axial side of the tapered rollers 13, a large-diameter annular portion 16 located on the other axial side of the tapered rollers 13, and a plurality of posts 17 connecting the small-diameter annular portion 15 and the large-diameter annular portion 16. The large-diameter annular portion 16 is provided with a recess 20 that opens toward the large end face 38 of the tapered rollers 13. The inner ring 12 has a large flange portion 24 on the other axial side that slides in contact with the large end face 38 of the tapered rollers 13.

[0060] If passed Figure 5 As explained, the first gap 51 between the large-diameter annular portion 16 and the outer ring 11 is smaller than the second gap 52 between the small-diameter annular portion 15 and the outer ring 11. Figure 2As shown, the large-diameter annular portion 16 has an inclined surface 31 on its outer periphery that expands in diameter as it moves toward the other side of the axial direction. The inclined surface 31 has a facing surface 32. The facing surface 32 is located on the axial side of the imaginary plane K1 of the side surface 81 on the other side of the axial direction of the outer ring 11, and is opposite to the inner circumferential surface 11a of the outer ring 11.

[0061] According to the tapered roller bearing 10 with the aforementioned structure, the first clearance 51 between the outer ring 11 and the large-diameter annular portion 16 is small. The large-diameter annular portion 16, like the outer ring raceway surface 21, has an inclined surface 31 that expands in diameter towards the other axial side, and this inclined surface 31 has a facing portion 32 opposite to the outer ring 11. Therefore, lubricating oil is difficult to flow out between the inner circumferential surface 11a of the outer ring 11 and the facing portion 32 of the large-diameter annular portion 16.

[0062] Furthermore, lubricating oil accumulates in the recess 20 of the large-diameter annular portion 16. Because the first gap 51 is small, the outer peripheral surface of the large-diameter annular portion 16 is close to the outer ring 11. Therefore, the large-diameter annular portion 16 becomes larger in the radial direction, which increases the volume of the recess 20.

[0063] Inside the bearing, between the outer ring 11 and the inner ring 12 and containing the tapered roller 13, lubricating oil has difficulty flowing out on the other side of the axial direction, and may accumulate more lubricating oil in the recess 20 of the large diameter annulus portion 16. The recess 20 is opposite to the large end face 38 of the tapered roller 13, so the lubricating oil in the recess 20 is supplied to the large end face 38. The lubricating oil supplied to the large end face 38 is then supplied between the large end face 38 and the large flange portion 24 of the inner ring 12 by the rotation of the tapered roller 13.

[0064] As described above, in the tapered roller bearing 10, it is easy to supply lubricating oil from the other side of the axial direction between the large flange portion 24 of the inner ring 12 and the large end face 38 of the tapered roller 13, which can improve the function of preventing sintering between them.

[0065] As described above, when the tapered roller bearing 10 rotates, the lubricating oil flows from one axial side to the other. Therefore, in the tapered roller bearing 10 of this embodiment, the first clearance 51 is smaller than the second clearance 52, but the sum of the first clearance 51 and the third clearance 53 is larger than the sum of the second clearance 52 and the fourth clearance 54. That is, according to this tapered roller bearing 10, the clearance on the downstream side of the lubricating oil flow direction is larger than the clearance on the upstream side. Therefore, when the bearing is rotating, the lubricating oil is less likely to remain inside the bearing, and the stirring resistance of the rotating cage 14 to the lubricating oil can be reduced.

[0066] In the tapered roller bearing 10 of this embodiment (refer to...) Figure 3The column 17 of the retainer 14 has a first outer surface 41 on its radially outer side. The first outer surface 41 causes the distance E1 between the first outer surface 41 and the inner circumferential surface 11a of the outer ring 11 to increase as it moves toward the other side of the axial direction.

[0067] According to this structure, when the centerline L of the rolling bearing 10 is horizontal, when the bearing is stopped, the space for accumulating lubricating oil between the column 17 and the outer ring 11 can be expanded on the bottom side of the rolling bearing 10. In particular, as described above, because the first clearance 51 is small, lubricating oil is difficult to flow out of the bearing, and a large amount of lubricating oil accumulates between the first outer surface 41 of the column 17 and the inner circumferential surface 11a of the outer ring 11. When the bearing starts to rotate, the lubricating oil in this space can be used for lubrication.

[0068] Furthermore, the column 17 has a wall surface 44 extending from the end of the first outer surface 41 on the axial side toward the outer ring 11. The wall surface 44 is positioned axially closer than the large-diameter annular portion 16. This structure allows lubricating oil flowing axially along the first outer surface 41 of the cage 14 to contact the wall surface 44 during bearing rotation. Figure 4 In the diagram, arrow Y indicates the flow of lubricating oil along the first outer surface 41. Through the wall 44, the flow direction of the lubricating oil changes to circumferential (direction of arrow X), making it easier to supply lubricating oil to the pocket 18 that holds the tapered roller 13 and the large end face 38 side of the tapered roller 13.

[0069] This improves the lubrication performance of the tapered roller bearing 10.

[0070] 〔other〕

[0071] The above embodiments are illustrative and not restrictive in all respects. The scope of the invention is defined not by the above embodiments but by the claims, and includes all modifications within the range equivalent to the structures described in the claims.

[0072] Label Explanation

[0073] 10 Tapered Roller Bearings

[0074] 11 Outer ring

[0075] 11a Inner circumferential surface

[0076] 12 Inner Circle

[0077] 13 Tapered rollers

[0078] 14. Cage

[0079] 15. Small-diameter annular portion

[0080] 16. Large-diameter annular section

[0081] 17 columns

[0082] 20 recess (second recess)

[0083] 21 Outer ring raceway surface

[0084] 22 Small flange portion

[0085] 24 Large flanges

[0086] 27 Inner ring raceway surface

[0087] 31 Inclined surface

[0088] 32 Relative face

[0089] 38 large end faces

[0090] 41. Outer surface

[0091] 41a end

[0092] 44 wall

[0093] 51 First gap

[0094] 52 Second gap

[0095] 53 Third gap

[0096] 54 Fourth gap

[0097] 81 Side View

[0098] K1 Imaginary Plane

Claims

1. A tapered roller bearing, comprising: The outer ring has an outer ring raceway surface that expands in diameter as it moves from one axial side toward the other axial side. The inner ring has an inner raceway surface that expands in diameter as it moves from one axial side toward the other axial side. Multiple tapered rollers, each having a large end face on the opposite axial side; and An annular cage holds the plurality of tapered rollers. The cage has: The small-diameter annular portion is located on one side of the axial direction of the tapered roller; The large-diameter annular portion is located on the other side of the axial direction of the tapered roller; and Multiple posts connect the small-diameter annular portion to the large-diameter annular portion. The inner ring has a large flange portion that slides in contact with the large end face. A recess is provided in the large-diameter annular portion that opens toward the large end face. The first gap is smaller than the second gap. The first gap is the gap between the large-diameter annular portion and the outer ring, and the second gap is the gap between the small-diameter annular portion and the outer ring. The large-diameter annular portion has an inclined surface on its outer circumference, which expands in diameter as it faces the opposite side of the axial direction. The inclined surface has a facing face that is located axially closer to an imaginary plane than the side surface on the other side of the outer ring along the axial direction, and is opposite to the inner circumferential surface of the outer ring. The column has the following characteristics on its radially outer side: The first outer surface is such that the distance between the first outer surface and the inner circumferential surface of the outer ring increases as it moves toward the other side of the axial direction. The second outer surface is continuous with the first outer surface and also continuous with the outer peripheral surface of the small-diameter annular portion. The wall extends from the end on the other side of the first outer surface toward the outer ring side. The column has an extended surface on its radially outer side, which is continuous with the wall surface via a bend and continuous with the inclined surface of the large-diameter annulus without a bend. The distance between the extended surface of the column and the inclined surface of the large-diameter annulus and the inner circumferential surface of the outer ring is smaller than the distance between the second outer surface and the inner circumferential surface of the outer ring.

2. The tapered roller bearing according to claim 1, wherein, When the gap between the outer peripheral surfaces of the large-diameter annular portion and the large flange portion is set as the third gap, and the gap between the small-diameter annular portion and the inner ring is set as the fourth gap,... The sum of the first gap and the third gap is greater than the sum of the second gap and the fourth gap.

3. The tapered roller bearing according to claim 1 or 2, wherein, The wall surface is positioned on the axial side of the larger diameter annular portion.

4. The tapered roller bearing according to claim 1 or 2, wherein, The inclined surface of the large-diameter ring has a facing face that is opposite to the inner circumferential surface of the outer ring and a non-facing face that is not opposite to the inner circumferential surface of the outer ring.

Images