CN219911512U - Tapered roller bearing - Google Patents

Abstract

The utility model provides a tapered roller bearing, which suppresses the action of tapered rollers by a cheap means which does not need to greatly change the structure of an iron plate retainer and does not damage the manufacturing easiness of an inner ring assembly, thereby being suitable for the use condition of lubrication by low-viscosity oil. The column part of the iron plate holder has a shape in which an outer surface (43 a) of the column part is recessed. Because of the concavity of the outer surface (43 a), the clearance between the tapered roller and the small diameter side of the pillar portion is smaller than the clearance between the tapered roller and the large diameter side of the pillar portion, and thus the operation of the tapered roller can be suppressed.

Description

Tapered roller bearing

Technical Field

The present utility model relates to tapered roller bearings.

Background

Conventionally, there is a tapered roller bearing in which a plurality of tapered rollers arranged between an inner ring and an outer ring are held at circumferential intervals by an iron plate holder.

In general, an iron plate holder for a tapered roller bearing is manufactured by punching a circular blank plate out of an iron-based plate, drawing the circular blank plate into a cup shape having a conical peripheral wall and a bottom plate, punching the peripheral wall to form a pocket, and subjecting a pillar portion to surface extrusion (for example, patent document 1).

In addition, the inner ring of the tapered roller bearing generally integrally has a raceway surface, a large flange, and a small flange. When an iron plate holder is used, plastic working is generally performed in which the small diameter side of the iron plate holder is pressed by a die to expand the diameter. In a state where tapered rollers are placed in the pockets of the expanded iron plate holder, the iron plate holder and the tapered rollers are combined with the inner ring from the small diameter side of the inner ring, and the tapered rollers are arranged on the raceway surface of the inner ring. Then, by plastic working (caulking working) in which the small diameter side of the iron plate holder is pressed by a die to return the above-described expanded diameter to the original position, the tapered rollers are prevented from falling off between the small diameter side annular portion of the holder and the small flange of the inner ring, whereby an inner ring assembly is constituted in which the holder, each tapered roller, and the inner ring are assembled in a non-separated state (for example, patent document 2).

The guide surface of the columnar portion of the iron plate holder, which is in contact with the tapered roller, is generally formed into a planar shape by performing surface extrusion processing on the circumferential end portion of the columnar portion (for example, patent document 3).

A gap for providing the pocket with radial and circumferential clearances is set between the pillar portion and the tapered roller. Based on the size of the gap, the allowable range of the operation in which the tapered roller can move relative to the retainer is determined. The final size of the gap is determined by the caulking process described above.

Patent document 1: japanese patent laid-open No. 2004-293698

Patent document 2: japanese patent application laid-open No. 2017-26001

Patent document 3: japanese patent No. 6786196

In recent years, in various devices such as automobile drive units (differential, transmission, EV reduction gear, HEV reduction gear, etc.), industrial machinery devices (robot reduction gear, construction machine, tractor, etc.), the viscosity of oil used is being accelerated for the purpose of improving efficiency, and it is difficult to lubricate rolling bearings incorporated therein. It is important to provide tapered roller bearings suitable for such severe conditions of use.

In the case of low viscosity oil, it is difficult to ensure proper oil film formation at the sliding contact portion between the large end face of the tapered roller and the large flange of the inner ring, and there is a concern that the above-described sliding contact portion will have increased resistance due to lubrication failure, and the tapered roller may be disturbed in operation (skew direction, tilt direction). In addition, there is a possibility that the tapered roller may be disturbed in operation due to other conditions of use of the bearing (amount of lubricant, load, rotational speed, temperature, use time, mixing of lubricant into foreign matters, etc.). If the tapered roller is significantly disturbed in operation, there is a concern that smooth rotation of the bearing is hindered due to disturbance of contact surface pressure at a rolling contact portion between the raceway surfaces of the inner and outer rings and the rolling surface of the tapered roller and heat generation at the sliding contact portion.

In the conventional iron plate holder in which the guide surface of the pillar portion is formed in a planar shape as in patent document 2, there is a limit in setting the gap between the pillar portion and the tapered roller, and thus the tapered roller cannot be restrained to such an extent that the operation (the skew direction, the inclination direction) of the tapered roller can be stabilized.

Disclosure of Invention

Accordingly, an object of the present utility model is to suppress the operation of tapered rollers by inexpensive means that does not require a great change in the structure of an iron plate retainer for a tapered roller bearing and does not impair the ease of manufacturing an inner ring assembly.

In order to solve the above problems, the present utility model provides a tapered roller bearing comprising: the tapered roller bearing includes an inner ring, an outer ring, a plurality of tapered rollers disposed between the inner ring and the outer ring, and an iron plate retainer for retaining the plurality of tapered rollers, wherein the inner ring integrally includes a raceway surface, a large flange, and a small flange, the iron plate retainer integrally includes a small-diameter side annular portion, a large-diameter side annular portion, and a plurality of pillar portions that divide a plurality of pockets between the small-diameter side annular portion and the large-diameter side annular portion, the pillar portions include outer surfaces that are continuous with an outer periphery of the small-diameter side annular portion and an outer periphery of the large-diameter side annular portion, and the pillar portions are shaped such that a gap between the tapered rollers and the small-diameter side of the pillar portions is smaller than a gap between the tapered rollers and the large-diameter side of the pillar portions.

According to the above configuration, since the clearance between the small diameter side of the pillar portion and the tapered roller is smaller than the clearance between the large diameter side of the pillar portion and the tapered roller based on the shape in which the outer surface of the pillar portion is recessed, when the operation of the tapered roller is disturbed under various bearing use conditions, the swing target side (small diameter side) of the tapered roller due to the operation can be borne in advance by the pillar portion, and the operation of the tapered roller can be suppressed. Further, since the clearance on the small diameter side is made smaller than the clearance on the large diameter side depending on the plastic deformation of the column portion which is slightly curved based on the shape of the concave outer surface of the column portion, it is possible to slightly change the shape of the die for caulking which ultimately determines the clearance at the time of assembling the inner ring assembly. Therefore, the iron plate holder can be provided with the characteristic of suppressing the tapered roller by an inexpensive means that does not require a great change in the structure of the iron plate holder and does not damage the ease of manufacturing the inner ring assembly.

When the distance between the outer surface of the column portion and the virtual straight line contacting the outer circumference of the small-diameter side annular portion and the outer circumference of the large-diameter side annular portion is set to a concave depth formed on the outer surface of the column portion, the deepest portion having the largest depth among the outer surfaces of the column portion may be formed on the small-diameter side of the column portion. Accordingly, the clearance on the small diameter side of the pillar portion, that is, on the side of the tapered roller toward the swing target can be made particularly small, and the operation of the tapered roller can be suppressed more effectively.

More preferably, the depth of the deepest portion is 10 μm or more and 200 μm or less. Accordingly, the effect of suppressing the operation of the tapered roller can be improved, and the clearance on the small diameter side is prevented from becoming too small, so that smooth rotation of the tapered roller is not hindered.

The distance between the outer surface of the column portion and the virtual straight line contacting the outer circumference of the small-diameter side annular portion and the outer circumference of the large-diameter side annular portion may be set to a concave depth formed on the outer surface of the column portion, and the maximum depth may be set to Dp on the outer surface of the column portion, wherein when (Φd/Φd) × (Lw/Dp) =the holder coefficient, the iron plate holder satisfies 100 < the holder coefficient < 1300. Accordingly, the above-described concavity can be effectively provided to the outer surface of the column portion with reasonable rigidity corresponding to the size of the iron plate holder.

The minimum value of the gap between the small diameter side of the pillar portion and the tapered roller may be 0.01mm or more and 0.12mm or less. Accordingly, excellent motion suppression performance of the tapered roller can be achieved, and strong collision between the tapered roller and the pillar portion at normal times can be avoided.

As described above, the retainer according to the present utility model can suppress the tapered roller by employing the above-described configuration, without requiring a significant change in the structure of the iron plate retainer for the tapered roller bearing, and without damaging the inexpensive means of manufacturing easiness of the inner ring assembly.

Drawings

Fig. 1 is a diagram showing an enlarged shape of an outer surface of a cylindrical portion of a tapered roller bearing according to an embodiment of the present utility model.

Fig. 2 is a cross-sectional view of the tapered roller bearing according to the embodiment of fig. 1.

Fig. 3 is a sectional view of the iron plate holder of fig. 2.

Fig. 4 is an enlarged partial cross-sectional view of the IV-IV line of fig. 2.

Fig. 5 is an enlarged partial cross-sectional view of the V-V line of fig. 2.

Fig. 6 is a diagram illustrating confusion of the operation of the tapered roller of fig. 2.

Fig. 7 is a diagram showing a first modification of the outer surface shape of the column portion according to the embodiment of fig. 1.

Fig. 8 is a diagram showing a second modification of the outer surface shape of the column portion according to the embodiment of fig. 1.

Fig. 9 is a diagram showing a third modification of the outer surface shape of the column portion according to the embodiment of fig. 1.

Description of the reference numerals

Inner ring; rolling surface; large flange; small flange; outer ring; tapered rollers; 40. an iron plate holder; small diameter side annular part; 42. large diameter side annular part; column part; external surface; 44. the pocket.

Detailed Description

Fig. 1 to 3 show a tapered roller bearing according to an embodiment of the present utility model.

The tapered roller bearing shown in fig. 2 includes: an inner ring 10, an outer ring 20, a plurality of tapered rollers 30 arranged between the inner ring 10 and the outer ring 20, and an iron plate holder 40 for holding the plurality of tapered rollers 30.

The inner ring 10 is constituted by a ring integrally having a tapered raceway surface 11 formed on the outer peripheral side thereof, a large flange 12 formed to have a larger diameter than the large diameter side edge of the raceway surface 11, and a small flange 13 formed to have a larger diameter than the small diameter side edge of the raceway surface 11.

The large flange 12 of the inner ring 10 supports and guides the large end surface of the tapered roller 30, which acts on the rolling surface 31, by thrust force directed toward the large diameter side in the axial direction during bearing rotation.

The small flange 13 of the inner ring 10 prevents the plurality of tapered rollers 30 from falling off the raceway surface 11 toward the small diameter side, and is used for a portion where the tapered rollers 30, the iron plate holder 40, and the inner ring 10 constitute a unit.

The outer ring 20 is constituted by a collar having a cone-shaped raceway surface 21 on the inner peripheral side thereof.

The tapered roller 30 is composed of rolling elements having rolling surfaces 31 formed in a tapered shape.

The plurality of tapered rollers 30 are arranged in a single row between the inner race 10 and the outer race 20.

The iron plate retainer 40 is an annular bearing member that holds the plurality of tapered rollers 30 at a predetermined pitch in the circumferential direction. As described in the background art, the iron plate holder 40 is formed by plastic working such as drawing and pocket punching with respect to a circular blank plate made of a ferrous plate material, and is subjected to caulking working when the inner ring 10, the plurality of tapered rollers 30, and the iron plate holder 40 are assembled into an inner ring assembly.

Here, fig. 2 shows a state in which the center lines of the inner ring 10, the outer ring 20, and the iron plate holder 40 coincide, and the center line will be hereinafter referred to as "bearing center axis CL1". Fig. 2 shows a positional relationship in which the center axes CL2 of the tapered rollers 30 and the center axes of the inner ring 10 and the outer ring 20, which are aligned with the bearing center axis CL1, are included in the same virtual axial plane, and the center axis CL2 of the tapered rollers 30 is located directly opposite to a point on the bearing center axis CL1 that is the conical apex of the inner and outer raceway surfaces 11 and 21. Hereinafter, the direction along the bearing center axis CL1 is referred to as an "axial direction", the direction orthogonal to the bearing center axis CL1 is referred to as a "radial direction", and the circumferential direction rotating around the bearing center axis CL1 is referred to as a "circumferential direction".

As shown in fig. 3, the iron plate holder 40 integrally has a small-diameter side annular portion 41, a large-diameter side annular portion 42, and a plurality of column portions 43 between the small-diameter side annular portion 41 and the large-diameter side annular portion 42. The iron plate holder 40 has a shape having a plurality of rotational symmetries substantially in the circumferential direction.

The small diameter side annular portion 41 has a circular outer periphery 41a extending in the circumferential direction. The large-diameter side annular portion 42 has an outer periphery 42a having a larger diameter than the outer periphery 41a of the small-diameter side annular portion 41. The inner diameter phid of the iron plate holder 40 coincides with the inner diameter of the small diameter side annular portion 41. The outer diameter phid of the iron plate holder 40 coincides with the outer diameter of the large-diameter side annular portion 42.

The plurality of pillar portions 43 are plate portions that divide a plurality of pockets 44 between the small-diameter side annular portion 41 and the large-diameter side annular portion 42. The plurality of column portions 43 are arranged at equal intervals in the circumferential direction. The pocket 44 is a space for accommodating one tapered roller 30.

The pillar portion 43 has an outer surface 43a located on the outer periphery of the iron plate holder 40, an inner surface 43b located on the inner periphery of the iron plate holder 40, and a guide surface 43c in contact with the tapered roller 30.

The guide surfaces 43c of the column portions 43 are formed at both circumferential end portions of each column portion 43. In the plastic working of the iron plate holder 40, the guide surface 43c is surface-pressed into a planar shape. That is, the guide surface 43c before the assembly of the inner ring assembly is started is planar.

Fig. 1 shows the shape of the outer surface 43a of the pillar portion 43. The shape of the outer surface 43a shown in the figure corresponds to the shape of the bus bar of the outer surface 43a. The shape of the figure is substantially continuous across the entire width of the outer surface 43a in the circumferential direction. A straight line Pc of the chain line in fig. 1 is a virtual straight line representing a virtual plane that is a boundary between the small diameter side of the column portion 43 and the large diameter side of the column portion 43. That is, the virtual straight line Pc represents a center position in fig. 1 that bisects the length of the column 43. The length of the pillar portion 43 corresponds to the length Lw of the pocket 44 shown in fig. 2. The length Lw of the pocket 44 corresponds to a distance between an imaginary plane in contact with a surface portion of the small-diameter side annular portion 41 facing the pocket 44 and an imaginary plane in contact with a surface portion of the large-diameter side annular portion 42 facing the pocket 44. The direction of the virtual straight line Pc shown in fig. 1 is a direction orthogonal to the central axis CL2 of the tapered roller 30 in the normal state shown in fig. 2. Further, since the shape of the outer surface 43a is exaggeratedly shown in fig. 1, the shape of the outer surface 43a shown in fig. 1 is greatly changed in aspect ratio in a direction in which the virtual straight line Pc extends and a direction orthogonal to the virtual straight line Pc, as compared with the shape of the outer surface 43a of the column portion 43 in fig. 3.

As shown in fig. 1 and 3, the outer surface 43a of the pillar portion 43 is continuous with the outer periphery 41a of the small-diameter side annular portion 41 and the outer periphery 42a of the large-diameter side annular portion 42.

As shown in fig. 1, the column portion 43 has a shape in which the outer surface 43a is recessed. The concave shape of the outer surface 43a is formed by caulking at the time of assembling the inner ring assembly. As the outer surface 43a is plastically deformed in a concave shape by the caulking process, the inner surface 43b of the pillar portion 43 shown in fig. 2 is plastically deformed so as to bulge out in accordance with the concave shape of the outer surface 43a, and therefore the pillar portion 43 is bent in accordance with the concave shape of the outer surface 43a shown in fig. 1. That is, by the caulking process, the curved portion of the pillar portion 43 in which the outer surface 43a is recessed approaches the tapered roller 30 in the radial direction, and as a result, the gap (radial gap) between the tapered roller 30 and the guide surface 43c (see fig. 3) included in the curved portion becomes smaller. As a result, as shown in fig. 2, 4, and 5, the tapered roller 30 and the small diameter side of the post 43 are radially directedGap (delta) ₁ And/2) is smaller than the radial clearance (delta) between the tapered roller 30 and the large diameter side of the pillar portion 43 ₂ /2). In other words, the clearance (δ of the small diameter side ₁ The minimum value in/2) is smaller than the gap (delta) on the large diameter side ₂ The minimum value in/2). In fig. 4 and 5, the gap (δ) is shown in an exaggerated manner ₁ /2)、(δ ₂ /2). The cross sections of fig. 4 and 5 show the small diameter side and the large diameter side, respectively, which are defined by the virtual straight line Pc, and the comparison is made by the magnitude relation of the minimum gaps in the ranges thereof.

As a gap (delta) ₁ /2)、(δ ₂ The measurement method of/2) includes, for example, the following methods: in a state where the iron plate holder 40, the tapered roller 30, and the inner ring 10 are assembled into a unit, the outer surface 43a of each of the column portions 43 of the iron plate holder 40 is provided on one of the small diameter side and the large diameter side to be measured with a measuring jig fixed in both the axial direction and the circumferential direction, the inner ring 10 is moved in the radial direction, the movement amount thereof is measured with a contact or non-contact measuring instrument, and the gap (δ) is calculated from the measured value ₁ /2)、(δ ₂ /2)。

In the rotation of the tapered roller bearing shown in fig. 2, the tapered roller 30 is brought into contact with the guide surface 43c (see fig. 3) of either one of the pair of column portions 43 located on both circumferential sides of the pocket 44 in accordance with a speed difference between the rotational speed of the iron plate holder 40 and the revolution speed of the tapered roller 30, and is brought into sliding contact with the large flange 12 of the inner ring 10 in a fluid lubrication state, whereby a stable posture is maintained. Depending on various bearing usage conditions, there is a possibility that the tapered roller 30 is not completely guided by the large flange 12 and the one guide surface 43c, and the tapered roller 30 is disturbed in operation, and the tapered roller 30 swings in the tilting direction or the tilting direction. As shown in fig. 6, the tapered roller 30 is tilted in a direction that forms an angle θ1 in the circumferential direction with respect to the normal direction (see fig. 2) and the tapered roller 30 is tilted in a direction that forms an angle θ2 in the radial direction with respect to the normal direction with respect to the central axis CL2″ of the tapered roller 30.

When the tapered roller 30 is disturbed in operation, the tapered roller 30 can swing in the skew direction or the tilt direction within the range of the gap (see fig. 4 and 5) between the pair of column portions 43 (see fig. 3) located on both circumferential sides thereof, but when the tapered roller 30 swings further, the small diameter side of the tapered roller 30 is restrained by the guide surfaces 43c (see fig. 3) of the pair of column portions 43, whereby the operation of the tapered roller 30 can be suppressed.

Here, a straight line L1 of the chain line shown in fig. 1 and 3 is a virtual straight line which is included in an arbitrary virtual plane including the central axis of the iron plate holder 40 and intersecting the outer surface 43a, and which is in contact with the outer periphery 41a of the small-diameter side annular portion and the outer periphery 42a of the large-diameter side annular portion 42 in the virtual plane. The distance between the virtual straight line L1 and the outer surface 43a of the pillar portion 43 is set to a concave depth formed in the outer surface 43a, and a portion having the maximum depth in the outer surface 43a is set to the deepest portion Pmax. The depth of the deepest portion Pmax is set to Dp. As shown in fig. 1, the depth Dp of the deepest portion Pmax is a distance between an imaginary straight line L1 and an imaginary straight line L2 when an imaginary straight line L2 parallel to the imaginary straight line L1 in the imaginary plane intersects the deepest portion Pmax of the outer surface 43a.

The concave portion of the outer surface 43a of the pillar portion 43 has a shape in which the depth becomes shallower as it approaches the outer periphery 41a of the small-diameter side annular portion 41 from the deepest portion Pmax and approaches the outer periphery 42a of the large-diameter side annular portion 42.

The deepest portion Pmax of the outer surface 43a of the column portion 43 shown in fig. 1 and 3 is formed to be located on the small diameter side (left side with respect to the straight line Pc) of the column portion 43. Therefore, at the time of caulking, the guide surface 43c (see fig. 3) is made particularly close to the small diameter side of the rolling surface 31 of the tapered roller 30 on the small diameter side of the pillar portion 43. Gap (delta) at small diameter side ₁ 2, see fig. 4) is substantially a virtual plane (a lead line indicating the maximum depth Dp) parallel to the virtual straight line Pc and including the deepest portion Pmax of the outer surface 43a. Thus, the clearance (δ) on the small diameter side is formed at the position on the small diameter side of the pillar portion 43, that is, on the swing target side of the tapered roller 30 on the opposite side to the large flange 12 (see fig. 2) of the inner ring 10 guiding the large diameter side of the tapered roller 30 ₁ 2, see fig. 4) has a particularly small extent with a width in the axial direction at a location remote from the large flange 12 (see fig. 2)Since the tapered roller 30 is highly present, the swing target side of the tapered roller 30 can be strongly restrained in advance. Therefore, the effect of suppressing the operation of the tapered roller 30 is particularly excellent.

The depth Dp of the deepest portion Pmax shown in fig. 1 is 10 μm or more and 200 μm or less, preferably 20 μm or more and 150 μm or less, and more preferably 30 μm or more and 100 μm or less. If the depth Dp of the deepest portion Pmax is less than 5 μm, the gap (δ) at the small diameter side ₁ 2, see fig. 4), the effect of suppressing the operation of the tapered roller 30 (see fig. 2 and 6) is small. If the particle diameter exceeds 300. Mu.m, the gap (delta) ₁ 2, see fig. 4), the contact force between the rolling surface 31 of the tapered roller 30 and the guide surface 43c is too high, and there is a possibility that smooth rotation of the tapered roller 30 is hindered.

Further, a radial gap (see fig. 4 and 5) is required between the pillar portion 43, the rolling surface 31 of the tapered roller 30, and the raceway surface 11 (see fig. 2). If the radial clearance is set too small to suppress the deflection and the movement in the oblique direction of the tapered roller 30, the swinging and turning operation of the iron plate holder 40 is insufficient as shown in fig. 2, and the columnar portion 43 and the rolling surface 31 always contact with each other to collide strongly, so that an oil film is broken at the rolling contact portion between the columnar portion 43 and the rolling surface 31, and there is a concern that the oil film is broken in advance. Therefore, the radial clearance (see fig. 4 and 5) is required to allow the iron plate holder 40 (see fig. 2) to swing to some extent. Taking this into consideration, the clearance (δ) on the small diameter side ₁ 2, see FIG. 4), is preferably 0.01mm to 0.12mm, more preferably 0.03mm to 0.10 mm. This can realize excellent motion suppression performance of the tapered roller 30 (see fig. 2 and 6), and allow a reasonable swinging rotation of the iron plate holder 40.

Here, (phid/phid) × (Lw/Dp) =the holder coefficient in the calculation using the outer diameter phid of the iron plate holder 40, the inner diameter phid of the iron plate holder 40, the length Lw of the pocket 44 (see fig. 3), and the depth Dp of the deepest portion Pmax (see fig. 1). The overall size of the iron plate holder 40 largely depends on the outer diameter phid, the inner diameter phid, and the length Lw of the pocket 44 (the pillar portion 43) of the iron plate holder 40. The plate thickness of the iron-based plate material is selected so that a reasonable rigidity can be obtained according to the overall size of the iron plate holder 40. The plate thickness affects the concave forming of the outer surface 43a of the column portion 43 by the caulking process and the narrowing of the gap. When the retainer coefficient of 100 < 1300 is satisfied, the above-described concavity can be effectively provided to the outer surface 43a (see fig. 1) of the pillar portion 43 so as to correspond to the tapered roller 30 while taking into consideration reasonable rigidity corresponding to the size of the iron plate retainer 40 (see fig. 3).

As described above, the tapered roller bearing includes: the inner race 10, the outer race 20, the plurality of tapered rollers 30 disposed between the inner race 10 and the outer race 20, and the iron plate retainer 40 retaining the plurality of tapered rollers 30, the inner race 10 integrally has the raceway surface 11, the large flange 12, and the small flange 13, the iron plate retainer 40 integrally has the small-diameter side annular portion 41, the large-diameter side annular portion 42, and the plurality of pillar portions 43 dividing the small-diameter side annular portion 41 and the large-diameter side annular portion 42 into a plurality of pockets 44 therebetween, and the pillar portions 43 have outer surfaces 43a (refer to fig. 1, 3 to 5) connected to the outer periphery 41a of the small-diameter side annular portion 41 and the outer periphery 42a of the large-diameter side annular portion 42, in particular, by employing gaps (δ) between the tapered rollers 30 and the small-diameter sides of the pillar portions 43 ₁ And/2) is smaller than the gap (delta) between the tapered roller 30 and the large diameter side of the pillar portion 43 ₂ 2) the column portion 43 having a shape in which the outer surface 43a of the column portion 43 is recessed is provided with a gap (δ) on the small diameter side based on the shape in which the outer surface of the column portion is recessed ₁ And/2) a gap (delta) smaller than the larger diameter side ₂ And/2), therefore, when the tapered roller 30 is disturbed in operation, the cylindrical portion 43 can carry the swing target side (small diameter side) of the tapered roller 30 in advance, and the operation of the tapered roller 30 can be suppressed.

In addition, the clearance (delta) of the small diameter side ₁ And/2) a gap (delta) smaller than the larger diameter side ₂ And/2) the post 43 is slightly bent based on the shape of the recess of the outer surface 43a of the post 43, so that it is possible to slightly change the shape of the die for caulking in the assembly of the inner ring assembly. Accordingly, in the tapered roller bearing, the manufacturing of the inner ring assembly is not damaged by the large change of the structure of the iron plate retainer 40 being unnecessaryThe iron plate holder 40 can be provided with characteristics of suppressing the operation of the tapered rollers 30 by an easy and inexpensive means.

Therefore, in this tapered roller bearing, the tapered roller 30 can be suppressed from operating by an inexpensive means that does not require a great change in the structure of the iron plate holder 40 and does not damage the ease of manufacturing the inner ring assembly.

In the tapered roller bearing, when the distance between the virtual straight line L1 contacting the outer periphery 41a of the small-diameter side annular portion 41 and the outer periphery 42a of the large-diameter side annular portion 42 and the outer surface 43a of the post 43 is set to the concave depth formed on the outer surface 43a of the post 43, the deepest portion Pmax having the maximum depth Dp in the outer surface 43a of the post 43 is formed on the small-diameter side of the post 43, whereby the gap (δ) on the small-diameter side of the post 43 (on the side of the tapered roller 30 on the swing target side) can be set to the small-diameter side ₁ And/2) is particularly small, so that the operation of the tapered roller 30 can be suppressed more effectively.

In addition, in the tapered roller bearing, the depth Dp of the deepest portion Pmax is 10 μm or more and 200 μm or less, whereby the effect of suppressing the operation of the tapered roller 30 can be improved, and the clearance (δ1/2) on the small diameter side is prevented from being excessively small so as not to hinder smooth rotation of the tapered roller 30.

In the tapered roller bearing, when the outer diameter of the iron plate holder 40 is Φd, the inner diameter of the iron plate holder 40 is Φd, the length of the pocket 44 is Lw, the distance between the virtual straight line L1 contacting the outer periphery 41a of the small-diameter side annular portion 41 and the outer periphery 42a of the large-diameter side annular portion 42 and the outer surface 43a of the post 43 is the concave depth formed on the outer surface 43a of the post 43, and the maximum depth is Dp in the outer surface 43a of the post 43, and when (Φd/Φd) × (Lw/Dp) =the holder coefficient, the iron plate holder 40 satisfies 100 < the holder coefficient < 1300, whereby the concave depth can be effectively given to the outer surface 43a of the post 43 with reasonable rigidity corresponding to the size of the iron plate holder 40.

In addition, in the tapered roller bearing, since the minimum value of the clearance (δ1/2) between the small diameter side of the pillar portion 43 and the tapered roller 30 is 0.01mm or more and 0.12mm or less, excellent operation suppressing performance of the tapered roller 30 can be achieved, and strong collision between the tapered roller 30 and the pillar portion 43 at normal times can be avoided.

In this tapered roller bearing, the deepest portion Pmax of the outer surface 43a of the pillar portion 43 is formed at a position near the outer periphery 41a of the small-diameter side annular portion 41 also in the small-diameter side portion of the pillar portion 43, whereby the tapered roller 30 can be suppressed from operating particularly on the side toward the swinging target, but the shape in which the outer surface of the pillar portion is recessed can take various shapes in addition to fig. 1. For example, as shown in fig. 7 to 9, the position of the deepest portion Pmax and the maximum depth Dp can be appropriately changed so as to obtain a desired tapered roller operation suppression performance based on the retainer coefficient described above. The concave shape of the outer surface of the pillar portion may be formed in a part of the length of the pillar portion or may be formed in the entire pillar portion.

All the embodiments disclosed herein are to be considered as examples and are not to be construed as limiting the utility model. The scope of the present utility model is defined not by the above description but by the appended claims, and is intended to include all modifications within the meaning and scope equivalent to the appended claims.

Claims (6)

1. A tapered roller bearing is provided with: an inner ring, an outer ring, a plurality of tapered rollers arranged between the inner ring and the outer ring, and an iron plate holder for holding the tapered rollers,

the inner ring is integrally provided with a raceway surface, a large flange and a small flange,

the iron plate holder integrally has a small-diameter side annular portion, a large-diameter side annular portion, and a plurality of pillar portions that divide a plurality of pockets between the small-diameter side annular portion and the large-diameter side annular portion, the pillar portions having outer surfaces that are continuous with an outer periphery of the small-diameter side annular portion and an outer periphery of the large-diameter side annular portion,

the tapered roller bearing is characterized in that,

the pillar portion has a shape in which an outer surface of the pillar portion is recessed so that a gap between the tapered roller and a small diameter side of the pillar portion is smaller than a gap between the tapered roller and a large diameter side of the pillar portion.

2. The tapered roller bearing according to claim 1, wherein,

when the distance between the outer surface of the column portion and the virtual straight line in contact with the outer circumference of the small-diameter side annular portion and the outer circumference of the large-diameter side annular portion is set to a concave depth formed on the outer surface of the column portion, the deepest portion having the largest depth among the outer surfaces of the column portion is formed on the small-diameter side of the column portion.

3. The tapered roller bearing according to claim 2, wherein,

the depth of the deepest portion is 10 μm or more and 200 μm or less.

4. A tapered roller bearing according to any one of claims 1 to 3,

the outer diameter of the iron plate holder is set to phid, the inner diameter of the iron plate holder is set to phid, the length of the pocket is set to Lw, the distance between an imaginary straight line contacting the outer periphery of the small-diameter side annular portion and the outer periphery of the large-diameter side annular portion and the outer surface of the column portion is set to a concave depth formed on the outer surface of the column portion, the maximum depth is set to Dp on the outer surface of the column portion, and the iron plate holder satisfies 100 < holder coefficient < 1300 when (phid/phid) × (Lw/Dp) =holder coefficient.

5. A tapered roller bearing according to any one of claims 1 to 3,

the minimum value of the clearance between the small diameter side of the pillar portion and the tapered roller is not less than 0.01mm and not more than 0.12 mm.

6. The tapered roller bearing according to claim 4, wherein,

the minimum value of the clearance between the small diameter side of the pillar portion and the tapered roller is not less than 0.01mm and not more than 0.12 mm.