JP2012237455A - Tapered roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a tapered roller bearing capable of improving incorporating property and further increasing a rated load by allowing the extension of the roller axial length.SOLUTION: The tapered roller bearing includes an inner ring, an outer ring 52, a tapered roller 53 disposed between the both so as to be capable of rolling, and a retainer 54 holding the tapered roller 53, in which a collar portion 56 is provided only on the large-diameter side of the inner ring. The retainer 54 includes a large-diameter-side annular portion 61, a small-diameter-side annular portion 62, and a column portion 63 mutually connecting the both. The large-diameter-side annular portion 61 includes an engaging portion 65. This provides the collar portion 56 of the inner ring with an engagemenet such that the assembled state can be maintained. When the holder is non-contact with the collar portion 56 in a neutral state and is non-contact with the collar portion 56 or contact with the collar portion 56 during operation, the inner surface of the engaging portion is put into a contact state with the bottom surface of a cutout portion 66 of the collar portion 56. A guide surface 71 for guiding the incorporation of the inner ring is provided at the inner diameter end portion of the outer surface 70 of the engaging portion 65.

Description

  The present invention relates to a tapered roller bearing.

  The driving force of the engine in the automobile is transmitted to the wheels via a power transmission system including any or all of a transmission, a propeller shaft, a differential, and a drive shaft.

  In this power transmission system, a tapered roller bearing having a high load capacity with respect to radial load and axial load, excellent impact resistance, and high bearing rigidity is often used as a bearing for supporting the shaft. As shown in FIG. 8, the tapered roller bearing generally includes an inner ring 2 having a conical raceway surface 1 on the outer peripheral side, an outer ring 4 having a conical raceway surface 3 on the inner peripheral side, and an inner ring 2. And a plurality of tapered rollers 5 disposed between the outer ring 4 and the outer ring 4, and a retainer 6 that holds the tapered rollers 5 at a predetermined circumferential interval.

  As shown in FIG. 9, the retainer 6 includes a pair of annular portions 6a and 6b and a column portion 6c that connects the annular portions 6a and 6b, and is formed between adjacent column portions 6c along the circumferential direction. The tapered roller 5 is accommodated in the pocket 6d.

  In this tapered roller bearing, the tapered roller 5 and the raceway surfaces 1 and 3 of the inner and outer rings 2 and 4 are in line contact, and the inner and outer ring raceway surfaces 1 and 3 and the roller center O are the axis P (see FIG. 8). Designed to match one point above (not shown).

  For this reason, when a load acts, the tapered roller 5 is pressed to the large end side. In order to receive this load, a flange portion 7 that protrudes toward the outer diameter side is provided on the larger diameter side of the inner ring 2. In addition, a flange 8 that protrudes also to the small end side of the inner ring 2 is provided so that the tapered roller 5 does not fall off to the small end side before the bearing is assembled in a machine or the like.

  In recent years, with the expansion of the interior space of vehicles, the engine room has been reduced, the engine output has been increased, and the transmission has been increased in stages to improve fuel efficiency. It is coming. In order to satisfy the life of the bearing in the usage environment, it was necessary to extend the life of the bearing.

  Against the above background, it can be proposed to increase the load capacity with the same dimensions and increase the life of the bearing by increasing the number of rollers or increasing the roller length. However, in the current structure, as described above, the inner ring 2 is provided with the flange portion (small rod) 8 on the small diameter side of the raceway surface for the reasons of bearing assembly. For this reason, there is a restriction by the flange portion 8 for increasing the length of the tapered roller 5. Each tapered roller 5 is supported by the cage 6 as described above, and the column portion 6c of the cage 6 is interposed between adjacent tapered rollers 5 along the circumferential direction. For this reason, there is a restriction by the column portion 6c even for the roller whose number of rollers is increased. Thus, there has been a limit in increasing the load capacity in the prior art.

  By the way, conventionally, there is an inner ring in which a small-diameter side collar (small collar) is omitted (Patent Document 1). If the collar portion on the small diameter side in the inner ring is omitted, the length of the tapered roller in the axial direction can be increased by that amount, and the load capacity can be increased. However, if the collar portion on the small diameter side is omitted in the inner ring, the tapered roller 5 falls off to the small end side before being assembled into a machine or the like. Therefore, in the inner ring, the small-diameter side collar (small collar) is omitted, as shown in FIG. 6, a hook that engages with the large-diameter side collar 7 is provided to prevent the tapered roller from falling. Provided.

  That is, the tapered roller bearing shown in FIG. 6 is a double-row tapered roller bearing, and is arranged between a pair of inner rings 21A and 21B, one outer ring 22, and inner rings 21A and 21B and the outer ring 22 so as to be freely rollable. A plurality of tapered rollers 23 and a pair of retainers 24A and 24B for holding the tapered rollers 23 at a predetermined circumferential interval are provided.

  Each retainer 24A, 24B connects the large diameter side annular part 25, the small diameter side annular part 26, and the large diameter side annular part 25 and the small diameter side annular part 26, similarly to the retainer 6 shown in FIG. And a column part 27. And the pocket 28 is formed between the column parts 27 adjacent to the circumferential direction, and the tapered roller 23 is hold | maintained at each pocket 28. FIG.

  The large-diameter side annular portion 25 is formed with a hook portion 30 disposed at a predetermined pitch along the circumferential direction. In this case, the hook portion 30 is formed of a flat rectangular piece that protrudes in the inner diameter direction from the outer end edge portion of the large-diameter side annular portion 25. Further, as shown in FIG. 7, a notch portion 32 is formed in the flange portion 31 of the inner ring 21 on the large diameter side of the outer diameter surface 31 a of the flange portion 31 of the inner ring 21, and the hook portion 30 is formed in the notch portion 32. Engage. At this time, there is a slight gap in the axial direction and the radial direction between the hook portion 30 and the notch portion 32, whereby the cage 24 is slightly movable in the axial direction and the radial direction. Here, when the cage 24 is in a neutral state with respect to the center of the shaft during operation (in a bearing assembly state), the hook portion 30 does not contact the flange portion 31 and does not contact the flange portion 31. There is a case where the bottom surface 31c of the flange 31 and the inner surface (inner diameter end) 33b of the hook portion 30 are in contact with each other, and the inner ring 21, the tapered roller 23, and the cage 24 are caught so that the assembled state can be maintained during non-operation. is there

Japanese Utility Model Publication No. 58-165324

Incidentally, in order to assemble the tapered roller bearing as shown in FIG. 6, first, the tapered roller 23 is accommodated in the pocket 28 of each cage 24. Thereafter, the inner ring 21 is fitted into the assembly of the cage 24 and the tapered roller 23. In other words, an assembly of the cage 24 and the tapered roller 23 is externally fitted to the inner ring 21.

  Then, a pair of combinations of the inner ring 21, the tapered roller 23, and the cage 24 is formed, and each combination is inserted from both openings of the outer ring 22, whereby the inner ring 21, the tapered roller 23, the cage 24, and the outer ring. Tapered roller bearings integrated with 22 can be assembled.

  However, it is necessary to fit the hook part 30 to the notch part 32 of the inner ring 21. At this time, the hook part 30 is elastically deformed and fitted. That is, when the hook 30 is fitted into the notch 32 of the inner ring 21, the inner diameter end 33 a of the outer surface 33 of the hook 30 contacts the inner surface 31 b of the flange 31 of the inner ring 21. However, since the inner diameter end portion 33a of the outer surface 33 of the hook portion 30 is a flat surface, when the inner ring 21 is assembled, the inner diameter end portion 33a of the outer surface 33 of the hook portion 30 is caught, which is extremely difficult to incorporate. For this reason, an excessive external force may act on the hook part 30 and the hook part 30 may be damaged.

  In view of the above problems, the present invention provides a tapered roller bearing that can be improved in assemblability and can be extended in the axial direction of the roller to increase the rated load. .

  The tapered roller bearing of the present invention includes an inner ring, an outer ring, a plurality of tapered rollers arranged to roll between the inner ring and the outer ring, and a cage that holds the tapered rollers at a predetermined circumferential interval. A tapered roller bearing provided with a flange that guides the tapered roller only on the large diameter side of the outer diameter surface of the inner ring, wherein the cage is made of resin, and includes a large diameter annular portion, a small diameter annular portion, The large-diameter side annular portion and the small-diameter-side annular portion are connected to each other, and the large-diameter-side annular portion is provided with a hook portion that can be hooked, and an inner ring is incorporated into the inner-diameter end of the outer surface of the hook portion. The guide surface part which guides is formed.

  According to the tapered roller bearing of the present invention, the raceway surface of the inner ring reaches the small diameter end from the collar part, and the collar part and the thinning part on the small diameter side of the inner ring that existed in the prior art are omitted. . For this reason, the raceway surface can be made large only in this omitted collar portion and fillet portion. Moreover, since the engaging part which engages with the collar part of the inner ring is provided in the cage, it is possible to prevent the tapered roller from falling off to the small end side.

  In particular, since the guide surface portion for guiding the incorporation of the inner ring is provided at the inner diameter end portion of the outer surface of the hook portion, the inner ring can be incorporated while being guided by the guide surface portion.

  The hooking part is not in contact with the collar part of the inner ring during operation, or when the hook part is in contact with the collar part of the inner ring, the inner surface of the hook part and the bottom surface of the notch part of the inner ring collar part are in contact with each other. Make sure that the inner ring, the tapered roller, and the cage are caught so that the assembled state can be maintained. As a result, during operation, the hook portion does not hinder the rotation, and can prevent the tapered roller from falling off to the small end before assembly or the like.

  The guide surface portion can be constituted by a tapered surface whose diameter is reduced inward in the axial direction.

  The cage is preferably made of resin, and the resin is preferably PPS (polyphenylene sulfide resin). PPS is a high-performance engineering plastic having a molecular structure in which phenyl groups (benzene rings) and sulfur (S) are alternately repeated. It is crystalline and has a continuous use temperature of 200 ° C. to 220 ° C., a high deflection temperature under a high load (1.82 MPa) of 260 ° C. and excellent heat resistance, and has a high tensile strength and bending strength. Since the shrinkage rate during molding is as small as 0.3 to 0.5%, the dimensional stability is good. Excellent in flame retardancy and chemical resistance. PPS can be broadly classified into three types: cross-linked, linear, and semi-cross-linked. The cross-linked type is a high molecular weight product obtained by cross-linking a low molecular weight polymer, and is mainly brittle and reinforced with glass fiber. The straight-chain type has a high toughness and has a high molecular weight without a crosslinking step in the polymerization stage. The semi-cross-linked type has the characteristics of both the cross-linked type and the straight chain type.

  The roller coefficient γ can exceed 0.94, or the window angle of the pocket of the cage can be 55 ° or more and 80 ° or less. Here, the roller coefficient γ is defined by the following equation. Further, the window angle of the pocket (between adjacent column portions along the circumferential direction) refers to an angle formed by a surface of the column portion that contacts the rolling surface of the tapered roller.

Roller coefficient γ = (Z · DA) / (π · PCD)
Here, Z: Number of rollers, DA: Roller average diameter, PCD: Roller pitch circle diameter

  The tapered roller bearing is preferably used to support a power transmission shaft of a self-propelled vehicle.

  In the tapered roller bearing of the present invention, the flange portion on the small diameter side of the inner ring, which has existed in the prior art, is omitted. For this reason, this omission part and weight reduction can be achieved. In addition, the raceway surface is enlarged only in the small diameter side flange portion and the omitted portion which are omitted, whereby the axial center length of the tapered roller can be increased, the load capacity can be improved, and a longer life can be achieved. it can.

  The hook can stably prevent the roller from separating from the inner ring. As a result, the incorporation can be improved. In particular, since the inner ring can be incorporated while being guided by the guide surface portion, it is not necessary to apply an excessive external force to the hook portion during the incorporation. For this reason, it can be prevented from causing plastic deformation beyond the damage or elastic limit of the hook portion, and the function of the hook portion can be stably exhibited. In addition, during operation, the hooking portion does not hinder rotation, and smooth rotation is possible.

  The guide surface portion can be constituted by a tapered surface whose diameter is reduced inward in the axial direction. As a result, the guide surface portion can be formed stably, and the reliability of incorporation into the inner ring can be improved.

  If the cage is made of an iron plate, the rigidity of the cage can be increased, and the tapered roller can be stably held over a long period of time. Moreover, it is excellent in oil resistance and can prevent material deterioration due to immersion in oil.

  However, since the cage made of resin is lighter in weight than the steel plate, is self-lubricating, and has a small friction coefficient, combined with the effect of the lubricating oil present in the bearing, It is possible to suppress the occurrence of wear due to the contact of. Further, since the resin cage is light and has a small coefficient of friction, it is suitable for reducing torque loss and cage wear at the time of starting the bearing. By using PPS (polyphenylene sulfide resin), which is highly resistant to oil, high temperature, and chemicals, in the cage, the life can be greatly extended.

  If the roller coefficient γ exceeds 0.94, the column width of the cage can be increased while avoiding contact between the outer ring and the cage in the neutral state. For this reason, it becomes possible to raise load capacity to the level of a full roller bearing (bearing which does not use a cage), without changing the bearing size. Thereby, the contact surface pressure can be reduced, the surface pressure in the stopped state is relaxed, and the fretting resistance is improved. In addition, a good contact state can be secured between the cage and the tapered roller, and the roller can be smoothly rotated.

  Further, by setting the cage window angle to 55 ° or more, it is possible to ensure a good contact state with the tapered roller, and by setting the cage window angle to 80 ° or less, the cage is pressed in the radial direction. The force is not increased and smooth rotation is obtained.

  For this reason, this tapered roller bearing is optimal for a bearing that supports the power transmission shaft of a self-propelled vehicle.

It is sectional drawing of the tapered roller bearing which shows embodiment of this invention. It is a principal part enlarged view of the said tapered roller bearing. It is sectional drawing which shows the assembly method of a tapered roller bearing. It is a principal part expanded sectional view of the said tapered roller bearing. It is sectional drawing which shows a modification in a guide surface part. It is sectional drawing of the conventional tapered roller bearing. It is sectional drawing of the holder | retainer of the said conventional tapered roller bearing. It is sectional drawing of the other conventional tapered roller bearing. It is a perspective view of the retainer of the tapered roller bearing shown in FIG.

Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  FIG. 1 shows a tapered roller bearing according to the present invention. This tapered roller bearing is a double row tapered roller bearing, and includes a pair of inner rings 51A and 51B, one outer ring 52, inner rings 51A and 51B, and an outer ring 52. A plurality of tapered rollers 53 disposed so as to be freely rollable therebetween, and a pair of retainers 54A and 54B that hold the tapered rollers 53 at a predetermined circumferential interval.

  Each inner ring 51 </ b> A, 51 </ b> B has a conical raceway surface 55 on its outer diameter surface, and a flange portion 56 is formed on the larger diameter side of the raceway surface 55 so as to protrude toward the outer diameter side. That is, the raceway surface 55 is formed from the flange portion 56 to the small diameter end, and does not have the flange portion on the small diameter side like the inner ring of the conventional tapered roller bearing. A corner portion 57 between the raceway surface 55 and the flange portion 56 is formed with a thin portion 57. Further, the inner surface (that is, the end surface on the small diameter side) 56b of the flange portion 56 is inclined by a predetermined angle α (see FIG. 2) with respect to a plane orthogonal to the bearing axis P.

  The flange portion 56 receives the large end surface 53a of the tapered roller 53 on its inner surface 56a, and receives an axial load through the tapered roller 53, and becomes a large flange for rotating and guiding the tapered roller 53. In addition, the conventionally provided gavel does not play a special role during the rotation of the bearing, and such a thing is omitted in the present invention.

  The outer ring 52 has a pair of tapered raceway surfaces 60, 60 on its inner diameter surface, and a plurality of tapered rollers 53 held by a cage 54 roll on this raceway surface 60 and the raceway surface 55 of the inner ring 51. Will do.

  In this tapered roller bearing, the tapered roller 53 and the raceway surfaces 55, 60 of the inner and outer rings 51, 52 are in line contact, and the inner / outer ring raceway surfaces 55, 60 and the roller center O are at one point on the axis P (see FIG. (Not shown).

  The cage 54 includes a large-diameter-side annular portion 61, a small-diameter-side annular portion 62, and a column portion 63 that connects the large-diameter-side annular portion 61 and the small-diameter-side annular portion 62. The column parts 63 are arranged at equal pitches along the circumferential direction, and the tapered rollers 53 are rotatably accommodated in accommodation parts (pockets) 64 provided between adjacent column parts 63 along the circumferential direction.

  A plurality of rectangular flat plate hooks 65 protruding in the inner diameter direction are arranged on the outer surface of the large-diameter annular portion 61 at a predetermined pitch along the circumferential direction. The hook 65 is engaged with the flange 56 of the inner ring 51. That is, a notch 66 is formed on the larger diameter side of the outer diameter surface 56 a of the flange portion 56 of the inner ring 51, and the hook 65 is engaged with the notch 66. At this time, there is a slight gap in the axial direction and the radial direction between the hook portion 65 and the notch portion 66, and the cage 24 can move slightly in the axial direction and the radial direction. That is, the hook 65 is not in contact with the flange 56 of the inner ring 51 without being in contact with the flange 56 when the cage 54 is in a neutral state with respect to the shaft center during operation (bearing assembled state). When contacting, the bottom surface 66a of the flange portion 56 of the inner ring 51 and the inner surface (inner diameter end) 65a of the hooking portion 65 are in contact with each other, and the inner ring 51, the tapered roller 53 and the cage 54 can be maintained in the assembled state when not in operation. There is a hook. For this reason, the notch dimension of the notch part 66 is determined by the relative approach amount that should be allowed between the inner diameter end 65a of the hook part 65 and the bottom surface 66a of the notch part 66, and the radial direction of the inner surface 72 of the hook part 65 and the notch part 66. It is set by the mutual approach amount to be allowed with the notch surface 66b.

  Further, a guide surface portion 71 that guides the incorporation of the inner ring 51 is formed at the inner diameter end portion of the outer surface (outer end surface) 70 of the hook portion 65. The guide surface portion 71 is a tapered surface 71a having a diameter that decreases inward in the axial direction, and the inclination angle is, for example, about 45 degrees.

  The window pushing angle (window angle) θ (see FIG. 3) of the column surface 63c of the column part 63 is, for example, 55 ° or more and 80 ° or less.

  The roller coefficient γ is set to exceed 0.94. Here, the roller coefficient γ is defined by the following equation. The window angle θ between the pockets (between adjacent column portions along the circumferential direction) refers to an angle formed by a surface of the column portion 63 that contacts the rolling surface of the tapered roller 53.

Roller coefficient γ = (Z · DA) / (π · PCD)
Here, Z: Number of rollers, DA: Roller average diameter, PCD: Roller pitch circle diameter

  Incidentally, the cage 54 is made of resin in the present invention. If the cage 54 is made of an iron plate, the rigidity of the cage can be increased, and the tapered roller 53 can be stably held over a long period of time. Moreover, it is excellent in oil resistance and can prevent material deterioration due to immersion in oil.

  As the resin, the synthetic resin material is preferably made of engineering plastic. An iron plate cage has the merit that it can be used without worrying about oil resistance (material deterioration due to immersion in oil). Further, if the resin cage is made of resin, that is, made of engineering plastic, it is not necessary to perform operations such as bottom expansion and caulking in the assembly of the bearing, so that it is easy to ensure the required dimensional accuracy. In addition, the cage made of resin is lighter than the steel plate, is self-lubricating, and has a small coefficient of friction. Therefore, combined with the effect of the lubricating oil in the bearing, It is possible to suppress the occurrence of wear due to the contact of. Further, since the resin cage is light and has a small coefficient of friction, it is suitable for reducing torque loss and cage wear at the time of starting the bearing. The engineering plastic (engineering plastic) is a synthetic resin that is mainly excellent in heat resistance and can be used in fields where strength is required. Further, a resin having increased heat resistance and strength is called a super engineering plastic, and this super engineering plastic may be used.

  Engineering plastics include polycarbonate (PC), polyamide 6 (PA6), polyamide 66 (PA66), polyacetal (POM), modified polyphenylene ether (m-PPE), polybutylene terephthalate (PBT), GF reinforced polyethylene terephthalate (GF- PET) and ultra high molecular weight polyethylene (UHMW-PE). Super engineering plastics include polysulfone (PSF), polyethersulfone (PES), polyphenylene sulfide (PPS), polyarylate (PAR), polyamideimide (PAI), polyetherimide (PEI), and polyetheretherketone. (PEEK), liquid crystal polymer (LCP), thermoplastic polyimide (TPI), polybenzimidazole (PBI), polymethylbenten (TPX), poly 1,4-cyclohexanedimethylene terephthalate (PCT), polyamide 46 (PA46), There are polyamide 6T (PA6T), polyamide 9T (PA9T), polyamide 11,12 (PA11,12), fluororesin, polyphthalamide (PPA) and the like.

  In particular, PPS (polyphenylene sulfide resin) is preferable. PPS is a high-performance engineering plastic having a molecular structure in which phenyl groups (benzene rings) and sulfur (S) are alternately repeated. It is crystalline, has a continuous use temperature of 200 ° C. to 220 ° C., a deflection temperature under a high load (1.82 MPa) of 260 ° C. or more, and is excellent in heat resistance, and has high tensile strength and bending strength. Since the shrinkage rate during molding is as small as 0.3 to 0.5%, the dimensional stability is good. Excellent in flame retardancy and chemical resistance. PPS can be broadly classified into three types: cross-linked, linear, and semi-cross-linked. The cross-linked type is a high molecular weight product obtained by cross-linking a low molecular weight polymer, and is mainly brittle and reinforced with glass fiber. The straight-chain type has a high toughness and has a high molecular weight without a crosslinking step in the polymerization stage. The semi-cross-linked type has the characteristics of both the cross-linked type and the straight chain type.

  Next, a method for assembling the tapered roller bearing will be described. First, the tapered rollers 53 are accommodated in the pockets 64 of the cages 54. Thereafter, the inner ring 51 is fitted into the assembly of the cage 54 and the tapered roller 53. In other words, an assembly of the cage 54 and the tapered roller 53 is externally fitted to the inner ring 51.

  That is, when the inner ring 51 is inserted into the combined body of the retainer 54 and the tapered roller 53 as shown in FIG. 3A, the outer diameter end of the inner surface 56 b of the flange portion 56 is first the guide surface portion 71. Abuts against the outer diameter end. If the inner ring is further inserted into the cage 54 from this state, the inner surface 56b of the flange portion 56 of the inner ring 51 slides on the guide surface portion 71 as shown in FIG. The hook portion 65 is elastically deformed and gets over the flange portion 56. When the hook portion 65 gets over the flange portion 56, the hook portion 65 is restored to the original state, and the flange portion 56 is in a state where the flange portion 56 is disposed between the roller 53 and the hook portion 65. .

  Thereafter, a pair of combinations of the inner ring 51, the tapered roller 53, and the cage 54 is formed, and the respective combinations are inserted into the outer ring 52 from both openings, whereby the inner ring 51, the tapered roller 53, the cage 54, and the outer ring. A tapered roller bearing integrated with 52 can be assembled. At this time, the end faces 68 and 68 on the small diameter side of the inner rings 51 and 51 are brought together. At this time, the axially outer end portion of the retainer 54 (that is, the outer surface 70 of the hook portion 66) is not projected outward in the axial direction from the large-diameter side end surfaces 69, 69 of the inner rings 51, 51.

  In the tapered roller bearing of the present invention, the flange portion on the small diameter side of the inner ring, which has existed in the prior art, is omitted. For this reason, this omission part and weight reduction can be achieved. In addition, the raceway surface is enlarged only in the small diameter side flange portion and the omitted portion which are omitted, whereby the axial center length of the tapered roller can be increased, the load capacity can be improved, and a longer life can be achieved. it can.

  The hook portion 65 can stably prevent the roller 53 from being detached from the inner ring 51. As a result, the incorporation can be improved. In particular, since the inner ring 51 can be incorporated while being guided by the guide surface portion 71, it is not necessary to apply an excessive external force to the hook portion 65 during the incorporation. For this reason, it can be prevented from causing plastic deformation beyond the damage and elastic limit of the hook portion 65, and the function of the hook portion 65 can be exhibited stably.

  The guide surface portion 71 is a tapered surface 71a whose diameter decreases inward in the axial direction, and the guide surface portion can be formed stably. As a result, the reliability of incorporation into the inner ring 51 can be improved.

  Thus, the tapered roller bearing is optimal for a bearing that supports the power transmission shaft of the self-propelled vehicle.

  Incidentally, the guide surface portion 71 may be as shown in FIG. That is, in FIG. 5 (a), it is a convex radius, and in FIG. 5 (b), it is a concave radius. Moreover, in the said embodiment, although it was set as the flat part in the internal diameter end 65a of the hook part 65, in such (c), such a flat part is not provided. The radius of curvature of the convex radius and the concave radius can be variously set within a range in which the incorporation of the inner ring 51 can be guided.

  Even the guide surface portion 71 as shown in FIG. 5 can guide the incorporation of the inner ring 51. For this reason, even if it uses such a holder | retainer 54, it can exhibit an effect similarly to the tapered roller bearing shown in FIG.

  As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications can be made. For example, the number of the hook portions 65 can be increased or decreased. In order to stably prevent the tapered roller 23 from falling, at least one is sufficient, and in consideration of strength and assemblability, it is preferable to arrange about 4 to 8 at a constant pitch along the circumferential direction. Moreover, you may comprise the hook part 65 in a ring part. In the embodiment, the notch 66 is opened in the end surface 69 on the large diameter side of the inner ring 51, but the annular groove formed in the outer diameter surface 56 a of the flange portion 56 without opening in the end surface 69. You may comprise.

  Further, when the guide surface portion 71 is configured by the tapered surface 71a, the inclination angle is not limited to 45 degrees, and various changes can be made within a range in which the incorporation of the inner ring 51 can be guided.

  This tapered roller bearing can be used for a differential or a transmission of an automobile, and can be used for various parts where a tapered roller bearing can be conventionally used. The tapered roller bearing may be a single row.

51 Inner ring 52 Outer ring 53 Tapered roller 54 Cage 56 Cage part 61 Large diameter side annular part 62 Small diameter side annular part 63 Column part 65 Hook part 70 Outer surface 71 Guide surface part 71a Tapered surface

Claims (7)

The inner ring includes an inner ring, an outer ring, a plurality of tapered rollers arranged to roll between the inner ring and the outer ring, and a retainer that holds the tapered rollers at a predetermined circumferential interval. A tapered roller bearing provided with a flange portion that guides the tapered roller only on the side,
The cage is made of resin, and includes a large-diameter-side annular portion, a small-diameter-side annular portion, and a column portion that connects the large-diameter-side annular portion and the small-diameter-side annular portion. A tapered roller bearing characterized in that a hook portion capable of being hooked is provided at a collar portion of the inner ring, and a guide surface portion for guiding the incorporation of the inner ring is formed at an inner diameter end portion of the outer surface of the hook portion.   The hook has a hook with which the inner ring, the tapered roller and the cage can be kept in an assembled state with respect to the collar portion of the inner ring. 2. The tapered roller bearing according to claim 1, wherein the hook portion and the bottom surface of the notch of the hook portion are in contact with each other when the hook portion is not in contact with or in contact with the flange portion. .   The tapered roller bearing according to claim 1, wherein the guide surface portion is a tapered surface having a diameter that decreases inward in the axial direction.   The tapered roller bearing according to any one of claims 1 to 3, wherein the resin used for the cage is PPS.   The tapered roller bearing according to any one of claims 1 to 4, wherein the roller coefficient γ exceeds 0.94.   The tapered roller bearing according to any one of claims 1 to 5, wherein a window angle of a pocket of the cage is set to 55 ° or more and 80 ° or less.   The tapered roller bearing according to any one of claims 1 to 6, wherein the tapered roller bearing supports a power transmission shaft of a self-propelled vehicle.

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