JP4912950B2 - Tapered roller bearing - Google Patents

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 for radial load and axial load and excellent in impact resistance is often used as a bearing for supporting the shaft. As shown in FIG. 5, the tapered roller bearing generally has 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. 6, 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. 5). 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 part (small collar) is omitted, as shown in FIG. 4, the hook part 30 that engages with the large-diameter side collar part 7 is held so that the tapered roller does not fall. The unit 24 is provided.

  That is, the tapered roller bearing shown in FIG. 3 includes inner rings 21 and 21, an outer ring 22, a plurality of tapered rollers 23 that are arranged to roll between the inner ring 21 and the outer ring 22, and the tapered rollers 23. And a cage 24 held at a predetermined interval.

  Similar to the cage 6 shown in FIG. 6, the cage 24 is a large-diameter side annular portion 25, a small-diameter-side annular portion 26, and a column portion 27 that connects the large-diameter-side annular portion 25 and the small-diameter-side annular portion 26. With. 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, a notch 32 is formed on the flange 31 of the inner ring 21 on the large diameter side of the outer diameter surface 31 a of the flange 31 of the inner ring 21, and the hook 30 is engaged with the notch 32. 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. That is, the hook portion 30 is in a non-contact state with the collar portion of the inner ring during operation and is hooked during non-operation.
Japanese Utility Model Publication No. 58-165324

  In the tapered roller bearing as shown in FIG. 3, the size of the hook portion 30 and the size of the hook portion 30 are considered in consideration of the amount of movement of the hook portion 30 during operation so that the hook portion 30 does not contact the flange portion 31 during operation. It is necessary to set the position. That is, when the hook portion 30 is interfered with the inner ring 21 in the axial direction during operation, a braking force is generated in the cage due to the restriction in the axial direction, and the contact force between the roller and the cage is increased. Unnecessary large stress is generated. For this reason, stable and smooth operation (rotation) cannot be achieved.

  Then, in order to set the size and position of the hook portion 30, as shown in FIG. 4, the relative approaching amount that should be permitted between the inner diameter end 30a of the hook portion 30 and the bottom surface 32a of the notch portion 32, and the hook It is set based on the mutual approach amount that should be permitted between the inner surface 33 of the portion 30 and the radial notch surface 32b of the notch portion 32. Here, the relative approach amount between the inner diameter end 30a of the hook portion 30 and the bottom wall 32a of the notch portion 32 is a radial play between the retainer 24 and the tapered roller 25 when the hook portion 30 is omitted ( It is the approach amount in (play). The mutual approach amount between the radial end surface 32b of the notch 32 and the hook portion 30 is the approach amount in the axial play (play) between the cage 24 and the tapered roller 25 when the hook portion 30 is omitted. It is. For this reason, it is not easy to set the size and position of the hook portion 30.

  Moreover, the collar part 31 needs to ensure the intensity | strength which receives the tapered roller 23. FIG. However, in order to ensure the strength, if the thickness (axial length) of the flange portion 31 is set large, the axial length of the raceway surface 35 of the inner ring 21 cannot be set long, and the smaller diameter side is set. Even if the buttocks (small ridges) are omitted, the rated load cannot be improved.

  In view of the above-mentioned problems, the present invention can ensure the strength of the collar part, can easily set the size and position of the hook part, and can extend the length in the roller axial direction. To provide a tapered roller bearing capable of increasing the 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 for guiding the tapered roller only on the large diameter side of the outer diameter surface of the inner ring, wherein the cage includes a large diameter annular portion, a small diameter annular portion, and a large diameter side. A column portion that connects the annular portion and the small-diameter-side annular portion, and the large-diameter-side annular portion is provided with a hook portion that protrudes toward the inner-diameter side, and on the outer end side in the axial direction of the outer-diameter surface of the flange portion A notch portion with which the hook portion is engaged is provided, and the relative approach amount to be permitted between the inner diameter end of the hook portion and the notch portion is the same or smaller between the inner diameter end of the hook portion and the bottom wall of the notch portion. provided radial clearance, and, between the notch radial end face and the hook portion of the inner surface of the radial end face Than the mutual approaching weight should be allowed between the hook portion is provided with a large axial clearance.

  According to the tapered roller bearing of the present invention, the flange portion and the fillet portion 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.

  Further, by providing a radial clearance between the inner diameter end of the hook portion and the bottom wall of the notch portion that is equal to or smaller than the allowable relative approach between the inner diameter end of the hook portion and the bottom wall of the notch portion. The contact of the inner diameter end of the hook portion with the bottom wall of the notch becomes possible. And the depth (diameter direction length) of a notch part can be set small, and the axial direction thickness of a collar part can be ensured.

By providing an axial gap between the radial end surface of the notch portion and the inner surface of the hook portion that is larger than the allowable mutual approach between the radial end surface and the hook portion, the radial end surface of the notch portion and Contact with the hook is lost.

  In the tapered roller bearing of the present invention, a clearance that allows contact between the inner diameter end of the hook portion and the bottom wall of the notch portion is formed, and a large clearance that does not contact the radial end surface of the notch portion and the inner surface of the hook portion. These settings are easy.

  The cage may be made of metal or resin. When using resin, it is preferable to use 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-crosslinked type has the characteristics of having both a crosslinked type and a linear type characteristic.

  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 depth (diameter length) of the notch can be reduced, and the axial thickness of the flange can be ensured. For this reason, sufficient intensity | strength to receive a tapered roller as a collar part is securable. In addition, it is possible to contact the bottom wall of the cutout portion at the inner diameter end of the hook portion, and the function of hooking the inner ring to the flange portion can be exhibited.

  Since there is no contact between the radial end surface of the notch and the hook, stable operation (rotational motion) is possible, and a high-quality bearing can be provided. Even if the inner diameter end of the hooking part contacts the bottom wall of the notch during operation (during rotation), since it is a radial interference, the generation of braking force on the cage is small, and the roller and cage The contact force does not increase.

  Further, the gap between the inner diameter end of the hook portion and the bottom wall of the notch portion, the gap between the radial end surface of the notch portion and the inner surface of the hook portion can be set relatively easily, and these settings are made. Easy. For this reason, the freedom degree of design of a cage | basket becomes large, it can manufacture easily and can aim at cost reduction.

  By making the cage made of 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.

  If the cage is made of resin, the cage weight is lighter than that made of iron plate, it is self-lubricating, and the friction coefficient is small, combined with the effect of the lubricating oil interposed in the bearing, It is possible to suppress the occurrence of wear due to contact with the outer ring. 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. In particular, the use of PPS (polyphenylene sulfide resin), which is highly resistant to oil, high temperature, and chemicals, in the cage can greatly extend the life.

  Hereinafter, an embodiment 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 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 56b, 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 are slight gaps in the axial direction and the radial direction between the hook portion 65 and the notch portion 66, and the cage 54 can move slightly in the axial direction and the radial direction.

  Between the inner diameter end 65a of the hook portion 65 and the bottom wall 66a of the notch portion 66, a radial clearance M1 smaller than the allowable relative approach amount between the inner diameter end 65a of the hook portion 65 and the notch portion 66 is provided. An axial gap M2 larger than the allowable mutual approach between the radial end surface 66b and the inner surface 72 of the hook 65 is provided between the radial end surface 66b of the notch 66 and the inner surface 72 of the hook 65. .

  The relative approach amount between the inner diameter end 65a of the hook portion 65 and the bottom wall 66a of the notch portion 66 is based on the play in the radial direction between the retainer 54 and the tapered roller 25 when the hook portion 65 is omitted. The approach amount. Further, the relative approaching amount that should be allowed is an amount of contact between the inner diameter end 65 a of the hook portion 65 and the bottom wall 66 a of the notch portion 66. For this reason, the inner diameter end 65a of the hook portion 65 and the bottom wall 66a of the notch portion 66 come into contact with each other.

  The mutual approach amount between the radial end surface 66b and the inner surface 72 of the hook portion 65 is an approach amount in the axial play (play) between the cage 54 and the tapered roller 25 when the hook portion 65 is omitted. Further, the relative approaching amount to be allowed is an amount of contact between the radial end face 66b and the hooking portion 65. For this reason, the radial direction end surface 66b and the hook part 65 do not contact.

  Incidentally, the cage 54 may be made of iron plate or resin. By using 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.

  When made of 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. At this time, it is necessary to fit the hook portion 65 to the notch portion 66 of the inner ring 51. In order to fit, the hook 65 may be elastically deformed and fitted.

  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 65) 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.

  Since the depth (radial length) of the notch can be reduced and the axial thickness of the flange 56 can be ensured, the flange 56 has sufficient strength to receive the tapered roller 53. Can be secured. Moreover, it becomes possible to contact the bottom wall 66a of the notch 66 of the inner diameter end 65a of the hook 65, and the function of hooking the inner ring 51 to the flange 56 can be exhibited.

  Since there is no contact between the radial end surface 66b of the notch 66 and the hook 65, stable operation (rotational motion) is possible, and a high-quality bearing can be provided. On the other hand, if the radial end surface 66b of the notch 66 comes into contact with the hook 65, the cage 54 will interfere with the inner ring 51 in the axial direction during operation. That is, a braking force is generated in the retainer 54 due to the axial restriction of the retainer 54, the contact force between the roller 53 and the retainer 54 is increased, and an unnecessary large stress is generated, which is stable and smooth. Operation (rotation) cannot be achieved. Even if the inner diameter end 65a of the hooking portion 65 contacts the bottom wall 66a of the notch 66 during operation (during rotation), the occurrence of braking force on the retainer 54 is small because of interference in the radial direction. The contact force between the roller 53 and the cage 54 does not increase.

  A clearance that allows contact between the inner diameter end 65a of the hook portion 65 and the bottom wall 66a of the notch portion 66 is formed, and a large gap that does not contact the radial end surface of the notch portion 66 and the inner surface 72 of the hook portion 66 is formed. These are easy to set up. For this reason, the freedom degree of design of a cage | basket becomes large, it can manufacture easily and can aim at cost reduction.

  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. The number of the hook portions 65 can be arbitrarily increased or decreased. In order to prevent the tapered rollers 23 from falling, at least one is sufficient, and considering strength and ease of incorporation, 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, the radial gap M1 can be arbitrarily set within a range smaller than the allowable relative approach amount, and the axial gap M2 can be arbitrarily set within a range larger than the allowable relative approach amount. For this reason, although M2> M1 in the embodiment, M2 = M1 or M2 <M1 depending on circumstances.

  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.

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 of the conventional tapered roller bearing. It is a principal part enlarged view of the said conventional tapered roller bearing. It is sectional drawing of the other conventional tapered roller bearing. FIG. 6 is a perspective view of a retainer of the tapered roller bearing shown in FIG. 5.

Explanation of symbols

51 Inner ring 52 Outer ring 54 Cage 55 Raceway surface 56 Ridge part 61 Large diameter side annular part 62 Small diameter side annular part 63 Column part 65 Hook part 65a Inner diameter end 66 Notch part 66a Bottom wall 66b Radial end face

Claims (4)

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 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, and protrudes toward the inner-diameter side in the large-diameter-side annular portion. And a notch for engaging with the hook is provided on the outer side in the axial direction of the outer diameter surface of the flange, and the hook is hooked between the inner diameter end of the hook and the bottom wall of the notch. A radial clearance that is equal to or smaller than the allowable relative approach between the inner diameter end of the portion and the notch, and between the radial end surface of the notch and the inner surface of the hook portion, A tapered roller bearing characterized in that an axial clearance larger than an allowable mutual approach amount with the hook portion is provided . The tapered roller bearing according to claim 1 , wherein the cage is made of metal . The tapered roller bearing according to claim 1 , wherein the cage is made of resin . The tapered roller bearing according to claim 3, wherein the resin used for the cage is PPS .

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