Tapered roller bearing

Abstract

This tapered roller bearing 10 comprises an outer ring 11, an inner ring 12, a plurality of tapered rollers 13, and an annular retainer 14. The retainer 14 has a small diameter annular section 15, a large diameter annular section 16, and a plurality of columns 17 that link the small diameter annular section 15 and the large diameter annular section 16. The inner ring 12 has a large flange section 24 that is in sliding contact with a large end surface 38. A recessed section 20 that opens toward the large end surface 38 is provided to the large diameter annular section 16. A first gap between the large diameter annular section 16 and the outer ring 11 is smaller than a second gap between the small diameter annular section 15 and the outer ring 11. The large diameter annular section 16 has, on the outer circumference, a sloped surface 31 the diameter of which widens toward the other side in the axial direction thereof. The sloped surface 31 has a facing surface section that is located further toward one side in the axial direction than a virtual plane that follows a side surface 81 on the other side in the axial direction of the outer ring 11, and faces the inner circumferential surface of the outer ring 11.

Description

Technical Field

[0001] The present disclosure relates to a tapered roller bearing.

Background Art

[0002] A tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers, and an annular cage for holding the plurality of tapered rollers. The 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 slidably contacts the large end face of the tapered roller (see, for example, Patent Document 1).

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In a tapered roller bearing, when the inner ring rotates, the large end face of the tapered roller slidably contacts the large flange portion of the inner ring. At the start of rotation, if there is little lubricating oil between the tapered roller and the large flange portion, or even in a rotating state, if the supplied lubricating oil is insufficient and the bearing is in a poor lubrication state, seizure is likely to occur between the tapered roller and the large flange portion.

[0005] In the tapered roller bearing disclosed in Patent Document 1, the gaps between the outer ring and the inner ring, respectively, and the large-diameter annular portion of the cage are small. Therefore, the lubricating oil inside the bearing where the tapered rollers are present hardly flows out to the outside of the bearing, and it becomes possible to prevent seizure between the tapered roller and the large flange portion by using the lubricating oil. As described above, in a tapered roller bearing, it is necessary to prevent seizure between the tapered roller and the large flange portion of the inner ring, and the development of new technical means capable of enhancing the seizure prevention function is desired.

Means for Solving the Problems

[0006] 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 that holds the plurality of tapered rollers, wherein the cage has a small diameter annular portion located on one axial side of the tapered roller, a large diameter annular portion located on the other axial side of the tapered roller, and a connecting portion between the small diameter annular portion and the large diameter annular portion. The outer ring has a plurality of columns, the inner ring has a large flange portion that slides in contact with the large end face, the large diameter ring portion is provided with a recess that opens toward the large end face, the first gap between the large diameter ring portion and the outer ring is smaller than the second gap between the small diameter ring portion and the outer ring, the large diameter ring portion has an inclined surface on its outer circumference that widens toward the other side in the axial direction, and the inclined surface has a facing surface portion that is located toward one side in the axial direction from a virtual plane along the other side surface of the outer ring in the axial direction and faces the inner circumferential surface of the outer ring. [Effects of the Invention]

[0007] The tapered roller bearing of this disclosure makes it possible to enhance the function of preventing seizure between the large flange portion of the inner ring and the large end face of the tapered roller. [Brief explanation of the drawing]

[0008] [Figure 1] Figure 1 is a cross-sectional view showing an example of a tapered roller bearing. [Figure 2] Figure 2 is an enlarged cross-sectional view showing the large-diameter annular portion of the retainer and its surrounding area. [Figure 3] Figure 3 is a cross-sectional view of the retainer through the column. [Figure 4] Figure 4 is an explanatory diagram showing the retainer and tapered roller viewed from the radially outer side, with the column at the center. [Figure 5] Figure 5 is an enlarged cross-sectional view showing the small-diameter annular portion and its surrounding area, as well as the large-diameter annular portion and its surrounding area of ​​the retainer. [Modes for carrying out the invention]

[0009] <Summary of Embodiments of the Invention Disclosed> The embodiments of the invention disclosed herein are outlined below.

[0010] (1) The tapered roller bearing of the present 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 that holds the plurality of tapered rollers, wherein the cage has a small diameter annular portion located on one axial side of the tapered roller, a large diameter annular portion located on the other axial side of the tapered roller, and the small diameter annular portion and the large diameter annular portion The outer ring has multiple connecting pillars, the inner ring has a large flange portion that slides in contact with the large end face, the large diameter annular portion is provided with a recess that opens toward the large end face, the first gap between the large diameter annular portion and the outer ring is smaller than the second gap between the small diameter annular portion and the outer ring, the large diameter annular portion has an inclined surface on its outer circumference that widens toward the other side in the axial direction, and the inclined surface has a facing surface portion that is located toward one side in the axial direction from a virtual plane along the other side surface of the outer ring in the axial direction and faces the inner circumferential surface of the outer ring.

[0011] In the tapered roller bearing described above, the first gap between the outer ring and the large-diameter annular portion of the cage is small. The large-diameter annular portion has an inclined surface that widens in diameter toward the other side in the axial direction, similar to the outer ring raceway surface, and this inclined surface has an opposing surface portion that faces the outer ring. Therefore, lubricating oil is less likely to leak out from between the inner circumferential surface of the outer ring and the opposing surface portion of the large-diameter annular portion. Lubricating oil is then stored in the recess of the large-diameter annular portion. Because the first gap is small, the outer surface of the large-diameter annular portion is close to the outer ring. As a result, the large-diameter annular portion can be made larger in the radial direction, and the volume of the recess can be increased. As described above, it becomes easier to supply lubricating oil from the other axial side between the large flange of the inner ring and the large end face of the tapered roller, thereby improving the function of preventing seizure between them.

[0012] (2) When the tapered roller bearing rotates, the lubricating oil flows from one axial side to the other axial side. Preferably, in the tapered roller bearing, the gap between the large diameter annular portion and the outer circumferential surface of the large flange portion is defined as the third gap, and the gap between the small diameter annular portion and the inner ring is defined as the fourth gap, in which case the sum of the first gap and the third gap is greater than the sum of the second gap and the fourth gap. As described above, the first gap is smaller than the second gap, but with the above configuration, the gap obtained by combining the first gap and the third gap is larger than the gap obtained by combining the second gap and the fourth gap. In other words, the gap on the downstream side in the direction of lubrication flow is larger than the gap on the upstream side. Therefore, when the bearing is rotating, the lubrication oil is less likely to accumulate inside the bearing, and the resistance to stirring the lubrication oil by the rotating cage is reduced.

[0013] (3) Preferably, the column has an outer surface on the radially outward side that increases the distance between it and the inner circumferential surface of the outer ring toward the other axial side. In this case, assuming the centerline of the rolling bearing is horizontal, when the bearing is stopped, it becomes possible to widen the space for accumulating lubricating oil between the column and the outer ring at the bottom of the rolling bearing. When the bearing starts rotating, the lubricating oil in that space can be used for lubrication.

[0014] (4) In the tapered roller bearing of (3) above, more preferably, the column has a wall surface extending toward the outer ring side from the other axial end of the outer surface, and the wall surface is provided on one axial side of the large diameter annular portion. In this case, when the bearing rotates, the lubricating oil that flows along the outer surface of the cage in the other axial direction comes into contact with the wall surface. This changes the direction of the lubricating oil flow to the circumferential direction, making it easier to supply lubricating oil to the pockets that hold the tapered rollers and to the large end faces of the tapered rollers.

[0015] <Details of Embodiments of the Invention in This Disclosure> Embodiments of the invention described herein will be explained below. [Regarding the overall structure of tapered roller bearings] FIG. 1 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 center line of the outer ring 11 and the center line of the inner ring 12 coincide with each other, and these center lines become the center line L of the tapered roller bearing 10. In the present embodiment, the inner ring 12 is a rotating ring that rotates together with a shaft not shown, and the outer ring 11 is a fixed ring attached to a housing not shown, but the outer ring 11 may be a rotating ring.

[0016] The direction along the center line L and the direction parallel to the center line L are defined as the "axial direction" of the tapered roller bearing 10. The left side in FIG. 1 is the "one side in the axial direction", and the right side in FIG. 1 is the "other side in the axial direction". The direction orthogonal to the center line L is defined as the "radial direction" of the tapered roller bearing 10. The direction along a circle centered on the center line L is defined as the "circumferential direction" of the tapered roller bearing 10.

[0017] The lubricating performance of the tapered roller bearing 10 is maintained by lubricating oil (oil). When the tapered roller bearing 10 rotates, the lubricating oil inside the bearing, which is between the outer ring 11 and the inner ring 12 and where the tapered rollers 13 are present, has an effect of flowing from one side in the axial direction to the other side in the axial direction. Due to this effect, the lubricating oil existing outside the bearing on one side in the axial direction of the tapered roller bearing 10 infiltrates into the bearing interior, passes through the bearing interior, and flows to the outside of the bearing on the other side in the axial direction. The tapered roller bearing 10 is lubricated by such lubricating oil.

[0018] The tapered roller 13 has a small end face 37 on one side in its axial direction and a large end face 38 on the other side in its axial direction. The outer ring 11 is cylindrical and has an outer ring raceway surface 21 on its inner peripheral surface. The outer ring raceway surface 21 expands in diameter from one side in the axial direction to the other side in the axial direction.

[0019] The inner ring 12 is cylindrical and has an inner ring raceway surface 27 on its outer circumference. The inner ring raceway surface 27 expands 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 circumference surface 25 of the large flange portion 24 is radially larger than the outer circumference surface 23 of the small flange portion 22. The large flange portion 24 has a flange surface 26 that slides in contact with the large end face 38 of the tapered roller 13.

[0020] The retainer 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 pillars 17 connecting the small-diameter annular portion 15 and the large-diameter annular portion 16. The region between the small-diameter annular portion 15 and the large-diameter annular portion 16, and between two adjacent pillars 17, 17 in the circumferential direction, becomes a pocket 18 that holds one tapered roller 13.

[0021] A first recess 19 is provided in the small-diameter annular portion 15, opening toward the small end face 37 of the conical roller 13. A second recess 20 is provided in the large-diameter annular portion 16, opening toward the large end face 38 of the conical roller 13. A column 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 column 17. Therefore, the radially inner portion 15b is relatively easy to deform. The column 17 is connected to both the radially outer portion 16a and the radially inner portion 16b of the large-diameter annular portion 16.

[0022] The disassembled state is defined as the state in which the outer ring 11 is removed from the assembled state shown in Figure 1. In the disassembled state, the pocket 18 of the retainer 14 holds the tapered roller 13, preventing it from falling out radially outward. To this end, the column 17 has a contact portion 28 that contacts the tapered roller 13 from the radially outward direction (see Figure 4). Figure 4 is an explanatory diagram showing the retainer 14 and the tapered roller 13 viewed from the radially outward direction with the column 17 at the center. The contact portion 28 is provided so as to protrude from the main body 17a of the column 17 on both sides in the circumferential direction.

[0023] As shown in Figure 1, the "reference state" is defined as the state in which the centerline of the cage 14 coincides with the centerline L of the tapered roller bearing 10. In the reference state, the small end face 37 of the tapered roller 13 and the small diameter annular portion 15 of the cage 14 are in contact. In the reference state, a small gap is provided in the radial direction between the tapered roller 13 that contacts the inner ring raceway surface 27 and the contact portion 28 of the cage 14. Within the range of this gap, the cage 14 can be displaced in the radial direction.

[0024] The retainer 14 has a guide surface 29 on a part of its outer circumferential surface that can contact the inner circumferential surface of the outer ring 11. The retainer 14 is positioned radially by the contact of the guide surface 29 with the inner circumferential surface (outer ring raceway surface 21) of the outer ring 11. In other words, the retainer 14 in this embodiment is a retainer for guiding the outer ring. A part of the large-diameter annular portion 16 (the opposing surface portion 32 described later, see Figure 2) and a part of the column 17 connected to that portion (the extended surface 35 described later, see Figure 2) form the guide surface 29.

[0025] Figure 2 is an enlarged cross-sectional view showing the large-diameter annular portion 16 of the retainer 14 and its surrounding area. The cross-sectional view shown in Figure 2 is a view of a cross-section that includes the center line L shown in Figure 1. In Figure 2, the hatched portion of the retainer 14 is the large-diameter annular portion 16.

[0026] The large-diameter annular portion 16 has an inclined surface 31 and an outer cylindrical surface 34 on its outer circumference. The inclined surface 31 is a surface that widens in diameter toward the other side in the axial direction. The inclined surface 31 has an opposing surface portion 32 that faces the inner circumferential surface 11a of the outer ring 11, and a non-opposing surface portion 33 that does not face the inner circumferential surface 11a of the outer ring 11. The opposing surface portion 32 is located to one side in the axial direction from a virtual plane K1 that runs along the side surface 81 on the other side in the axial direction of the outer ring 11, and faces the inner circumferential surface 11a of the outer ring 11. The non-opposing surface portion 33 is located to the other side in the axial direction from the virtual plane K1, and does not face the inner circumferential surface 11a of the outer ring 11. The opposing surface portion 32 and the non-opposing surface portion 33 are continuously provided on the outer circumference of the large-diameter annular portion 16. In the cross-section shown in Figure 2, the non-opposing surface portion 33 is provided along the extension of the opposing surface portion 32.

[0027] The outer cylindrical surface 34 will now be described. The outer cylindrical surface 34 is a surface that is continuous with the non-opposing surface portion 33 via the bent portion 36. The outer cylindrical surface 34 is a surface whose inclination angle with respect to the center line L (see Figure 1) is smaller than that of the inclined surface 31, or a surface that aligns with a virtual cylindrical surface with respect to the center line L (see Figure 1). Like the inclined surface 31, the outer cylindrical surface 34 is a surface that is continuous in the circumferential direction.

[0028] The column 17 has an extended surface 35 on the other axial side that is continuous with the inclined surface 31. The inclination angle with respect to the center line L (see Figure 1) is the same for the extended surface 35 and the inclined surface 31. The inclined 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 portion 32 and the extended surface 35 form a guide surface 29 that can contact the outer ring 11.

[0029] Figure 3 is a cross-sectional view of the plane passing through the center line L and the column 17 of the retainer 14. The column 17 has a first outer surface 41 and a second outer surface 42 on its radially outward side. The first outer surface 41 has a shape along a first virtual tapered surface that decreases in diameter in one axial direction, but is a surface that increases the gap E1 between it and the inner circumferential surface 11a of the outer ring 11 in the other axial direction. The first outer surface 41 is located on one axial side of the inclined surface 31 and the extended surface 35.

[0030] The second outer surface 42 has a shape that follows a second virtual tapered surface that narrows in diameter in one axial direction. With respect to the center line L, 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. In other words, the second outer surface 42 is a surface for which the distance E2 between it and the inner circumferential surface 11a of the outer ring 11 is constant. The first outer surface 41 and the second outer surface 42 are continuous via a bent portion 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.

[0031] The column 17 has a wall surface 44 extending toward the outer ring 11 from the axial end 41a of the first outer surface 41 on the other side. As shown in Figures 3 and 4, the wall surface 44 is located on one side in the axial direction relative to the large-diameter annular portion 16. The wall surface 44 is the surface facing one side in the axial direction. The wall surface 44 is continuous with the extension surface 35 via the bent portion 45.

[0032] Figure 5 is an enlarged cross-sectional view showing the small-diameter annular portion 15 and its surrounding area, and the large-diameter annular portion 16 and its surrounding area of ​​the retainer 14. In the standard state, the gap formed between the large-diameter annular portion 16 and the other axial end 61 of the outer ring 11 is called the "first gap 51". In the standard state, the gap formed between the small-diameter annular portion 15 and the one axial end 62 of the outer ring 11 is called the "second gap 52". In the standard state, the gap formed between the large-diameter annular portion 16 and the large flange portion 24 of the inner ring 12 is called the "third gap 53". In the standard state, the gap formed between the small-diameter annular portion 15 and the small flange portion 22 of the inner ring 12 is called the "fourth gap 54".

[0033] The radial dimension of the first gap 51 is "R1", and 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". Note that the dimensions R1, R2, R3, and R4 are the dimensions of the smallest radial portion in each gap.

[0034] 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). In the cross section shown in FIG. 2, in the reference state, the inner peripheral surface 11a of the outer ring 11 and the inclined surface 31 of the large-diameter annular portion 16 are parallel, and the first gap 51 is between these inner peripheral surface 11a and the inclined surface 31, and the radial dimension in the first gap 51 is R1.

[0035] In FIG. 5, each of the first gap 51 and the second gap 52 is formed continuously in the circumferential direction. For this reason, a first annular gap 56 is formed between the large-diameter annular portion 16 and the end portion 61 of the outer ring 11 by the first gap 51. A second annular gap 57 is formed between the small-diameter annular portion 15 and the end portion 62 of the outer ring 11 by the second gap 52. 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.

[0036] The sum of the first gap 51 and the third gap 53 is larger 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 larger than the sum of the radial dimension R2 of the second gap 52 and the radial dimension R4 of the fourth gap 54 (R + R3 > R2 + R4).

[0037] Each of the third gap 53 and the fourth gap 54 is formed continuously in the circumferential direction. For this reason, a third annular gap 58 is formed between the large flange portion 24 of the inner ring 12 and the large-diameter annular portion 16 by the third gap 53. A fourth annular gap 59 is formed between the small flange portion 22 of the inner ring 12 and the small-diameter annular portion 15 by the fourth gap 54. 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 larger 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).

[0038] [Regarding the tapered roller bearing 10 of the present embodiment] As described above, the tapered roller bearing 10 of this embodiment (see Figure 1) comprises an outer ring 11, an inner ring 12, a plurality of tapered rollers 13, and an annular cage 14 that holds the plurality of tapered rollers 13. 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 pillars 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 roller 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 roller 13.

[0039] As explained in Figure 5, 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. As shown in Figure 2, the large-diameter annular portion 16 has an inclined surface 31 on its outer circumference that widens in diameter toward the other axial direction. The inclined surface 31 has an opposing surface portion 32. The opposing surface portion 32 is located axially to one side of a virtual plane K1 that runs along the side surface 81 of the outer ring 11 on the other axial side, and faces the inner circumferential surface 11a of the outer ring 11.

[0040] In the tapered roller bearing 10 having the above configuration, the first gap 51 between the outer ring 11 and the large-diameter annular portion 16 is small. The large-diameter annular portion 16 has an inclined surface 31 that widens in diameter toward the other side in the axial direction, similar to the outer ring raceway surface 21, and this inclined surface 31 has an opposing surface portion 32 that faces the outer ring 11. Therefore, lubricating oil is less likely to leak out from between the inner circumferential surface 11a of the outer ring 11 and the opposing surface portion 32 of the large-diameter annular portion 16.

[0041] Lubricating oil is then stored in the recess 20 of the large-diameter annular portion 16. Because the first gap 51 is small, the outer surface of the large-diameter annular portion 16 is close to the outer ring 11. As a result, the large-diameter annular portion 16 is made larger in the radial direction, and the volume of the recess 20 can be increased. Within the bearing, between the outer ring 11 and the inner ring 12 where the tapered roller 13 is located, the lubricating oil is less likely to flow out on the other axial side, and more lubricating oil can be stored in the recess 20 of the large-diameter annular portion 16. Since the recess 20 faces the large end face 38 of the tapered roller 13, 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 as the tapered roller 13 rotates.

[0042] As described above, in the tapered roller bearing 10, it becomes easier to supply lubricating oil from the other axial side between the large flange portion 24 of the inner ring 12 and the large end face 38 of the tapered roller 13, thereby improving the function of preventing seizure between them.

[0043] As described above, when the tapered roller bearing 10 rotates, the lubricating oil flows from one axial side to the other axial side. In this embodiment of the tapered roller bearing 10, the first gap 51 is smaller than the second gap 52, but the sum of the first gap 51 and the third gap 53 is larger than the sum of the second gap 52 and the fourth gap 54. In other words, with this tapered roller bearing 10, the gap on the downstream side in the direction of lubricating oil flow is larger than the gap on the upstream side. Therefore, when the bearing is rotating, the lubricating oil is less likely to accumulate inside the bearing, and the stirring resistance of the lubricating oil by the rotating cage 14 is reduced.

[0044] Furthermore, in the tapered roller bearing 10 of this embodiment (see Figure 3), the column 17 of the cage 14 has a first outer surface 41 on its radially outward side. The first outer surface 41 increases the gap E1 between it and the inner circumferential surface 11a of the outer ring 11 toward the other side in the axial direction. This configuration allows for a larger space for accumulating lubricating oil between the column 17 and the outer ring 11 at the bottom of the rolling bearing 10 when the bearing is stopped, assuming the centerline L of the rolling bearing 10 is horizontal. In particular, as mentioned above, because the first gap 51 is small, the lubricating oil is less likely to flow out of the bearing, and a large amount of lubricating oil is accumulated 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 that space can be used for lubrication.

[0045] Furthermore, the column 17 has a wall surface 44 extending toward the outer ring 11 from the axial end of the first outer surface 41 toward the other end. The wall surface 44 is located axially toward one side of the large-diameter annular portion 16. With this configuration, when the bearing rotates, the lubricating oil that flows axially toward the other side along the first outer surface 41 of the cage 14 hits the wall surface 44. In Figure 4, the flow of lubricating oil along the first outer surface 41 is indicated by arrow Y. The wall surface 44 changes the direction of the lubricating oil flow to the circumferential direction (direction of arrow X), making it easier to supply lubricating oil to the pocket 18 that holds the tapered roller 13 and to the large end face 38 side of the tapered roller 13. Based on the above, it is possible to improve the lubrication performance of the tapered roller bearing 10.

[0046] 〔others〕 The embodiments described above are illustrative and not restrictive in all respects. The scope of the present invention is indicated by the claims rather than by the embodiments, and includes all modifications within the scope of equivalence to the configurations described in the claims. [Explanation of Symbols]

[0047] 10 tapered roller bearing 11 Outer ring 11a Inner surface 12 Inner Ring 13 yen water droplet 14 Cage 15 Small diameter ring section 16 Large diameter annular section 17 pillars 20. Recess (Second recess) 21 Outer ring raceway surface 22 Small guard section 24 Otsubabe 27 Inner ring raceway surface 31 Slope 32 Opposing surface part 38 Big end face 41 External surface 41a End 44 Wall surface 51 First gap 52 Second gap 53 Third gap 54 The Fourth Gap 81 Side view K1 Virtual Plane

Claims

1. An outer ring having an outer ring raceway surface that widens in diameter from one axial side to the other axial side, An inner ring having an inner ring raceway surface that widens in diameter from one axial side to the other axial side, Multiple tapered rollers having a large end face on the other side in the axial direction, It comprises an annular holder that holds the plurality of tapered rollers, The aforementioned retainer is, The small diameter annular portion located on one axial side of the aforementioned tapered roller, A large-diameter annular portion located on the other axial side of the aforementioned tapered roller, It has a plurality of pillars connecting the small-diameter annular portion and the large-diameter annular portion, The inner ring has a large flange portion that slides in contact with the large end surface, The large-diameter annular portion is provided with a recess that opens toward the large end face, The first gap between the large-diameter annular portion and the outer ring is smaller than the second gap between the small-diameter annular portion and the outer ring. The aforementioned large-diameter annular portion has an inclined surface on its outer circumference that expands in diameter toward the other side in the axial direction, The inclined surface has a facing surface portion that is located on one axial side of a virtual plane along the other axial side of the outer ring and faces the inner circumferential surface of the outer ring. The aforementioned column extends radially outward, A first outer surface that increases the distance between the outer ring and the inner circumferential surface in the axial direction toward the other side, A second outer surface which is continuous with the first outer surface and continuous with the outer circumferential surface of the small diameter ring portion, A wall surface extending toward the outer ring side from the other axial end of the first outer surface, It has an extension surface that is continuous with the wall surface via a bent portion and continuous with the opposing surface of the large-diameter annular portion without passing through the bent portion, The extended surface of the column, which is continuous with the wall surface via a bent portion, and the opposing surface of the large-diameter annular portion, which is continuous with the extended surface without a bent portion, face the inner circumferential surface of the outer ring, and the distance between the extended surface and the opposing surface 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. Tapered roller bearing.

2. The gap between the large-diameter annular portion and the outer circumferential surface of the large flange portion is defined as the third gap. When the gap between the small-diameter annular portion and the inner ring is defined as the fourth gap, The tapered roller bearing according to claim 1, wherein 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 claim 2, wherein the wall surface is provided on one axial side of the large-diameter annular portion.

4. The tapered roller bearing according to claim 1 or 2, wherein the inclined surface of the large-diameter annular portion has an opposing surface portion that faces the inner circumferential surface of the outer ring and a non-opposing surface portion that does not face the inner circumferential surface of the outer ring.

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