JP2008202747A - Double-row tapered roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double-row tapered roller bearing having compacter, more inexpensive and simple construction for preventing the separation of an inner ring. <P>SOLUTION: The double-row tapered roller bearing 1 comprises a seal 6 consisting of an annular seal plate 7 and a slinger 8 arranged opposing each other. The slinger 8 has a cylindrical portion 8a and a rising plate portion 8b fitted to the outer diameter of the inner ring 3. The seal plate 7 consists of a core metal 9 having a cylindrical portion 9a and a rising plate portion 9b internally fitted to an outward member 2, an inner diameter portion 9c extending to the inward side of the bearing, and a locking portion 9d protruded to the side of the inner ring 3, and a seal member 10 joined to the core metal 9 and having a side lip 10a to be put in slide contact with the rising plate portion 8b of the slinger 8, and a radial lip 10b to be put in slide contact with the cylindrical portion 8a. A distance e1 between a large end face 4a of a tapered roller 4 and the locking portion 9d of the core metal 9 is set to be shorter than a distance between a cage 5 and the core metal 9 so that the radial lip 10b is free from fall-off from the cylindrical portion 8a of the slinger 8. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a double-row tapered roller bearing for a wheel for rotatably supporting a wheel of an automobile or the like, and more particularly, a double-generation tapered roller bearing having a pair of inner rings and preventing separation of these inner rings. The present invention relates to a row tapered roller bearing.

  Conventionally, a wheel bearing device for supporting a wheel of an automobile or the like is such that a hub wheel for mounting a wheel is rotatably supported via a double row rolling bearing. In addition, a double-row angular ball bearing having a desired bearing rigidity, exhibiting durability against misalignment, and having a small rotational torque from the viewpoint of improving fuel efficiency is often used. On the other hand, double row tapered roller bearings are used in vehicles such as off-road cars and trucks that have a heavy vehicle body weight.

  As shown in FIG. 5, the conventional double-row tapered roller bearing 50 has an outer ring 51 in which double-row outer rolling surfaces 51a and 51a are formed on the inner periphery, and these double-row outer rolling surfaces 51a on the outer periphery. , 51a, a pair of inner rings 52, 52 formed with inner rolling surfaces 52a, 52a, and double row tapered rollers accommodated between the rolling surfaces via cages 53, 53 so as to roll freely. 54, 54, seals 55, 55 attached to the opening of the annular space formed between the outer ring 51 and the inner ring 52, and an annular formed on the inner diameter surface on the contact surface side between the inner rings 52, 52. And a separation preventing member 57 fitted in the holding recess 56. A first gap 58 having a predetermined width A is provided between the end face of the cage 53 and the end face of the seal 55.

  As shown in FIG. 6, the separation preventing member 57 has a U-shaped cross section by pressing from a steel plate, is formed in an annular shape as a whole, and is formed with a bent portion 59 that is fitted into the holding recess 56 of the inner ring 52. ing. Further, a second gap 60 having predetermined widths d1 and d2 is provided between the bent portion 59 of the separation preventing member 57 and the wall surface of the holding recess 56, and an assembly of the inner ring 52, the tapered roller 54 and the cage 53. Is configured to be slightly movable in the direction of the axis 61. The first gap 58 when the double-row tapered roller bearing 50 is assembled is larger than the value obtained by subtracting the minimum width of the width C between the wall surfaces of the holding recess 56 from the width D between the bent portions 59. (A> D−C = d1 + d2).

The double row tapered roller bearing 50 is assembled by incorporating an assembly of the inner ring 52, the tapered roller 54 and the cage 53 into the outer ring 51. For example, when the assembly of the inner ring 52, the tapered roller 54 and the cage 53 receives a force in the direction of the axis 61 during the conveyance of the product or the like, it slightly moves in the direction of the axis 61 and the width of the first gap 58 The width C (widths d1, d2) between A and the wall surface of the holding recess 56 changes. However, the width C between the wall surfaces of the holding recess 56 is at most the width D between the bent portions 59. Therefore, even if the width A of the first gap 58 and the width C between the wall surfaces of the holding recess 56 change. , A> D−C = d1 + d2, so even when the assembly of the inner ring 52, the tapered roller 54 and the retainer 53 moves in the direction of the axle 62, the end face of the retainer 53 and the seal 55 Contact with the end face can be prevented.
JP 2002-310175 A

  However, in this conventional double-row tapered roller bearing 50, the separation preventing member 57 is fitted into the holding recess 56 formed on the inner diameter surface of the inner ring 52 to prevent the inner ring 52 from moving in the direction of the axis 61. This not only increases the number of parts of the separation preventing member 57, but also increases the number of processing steps for forming the holding recess 56 in the inner ring 52, and further increases the number of assembly steps for fitting the separation preventing member 57, There was a problem of high costs.

  Further, since this type of double-row tapered roller bearing 50 for a wheel is required to be compact, it is difficult to ensure a sufficient thickness and width space to form the holding recess 56 in the inner ring 52. Therefore, conventionally, it has been necessary to employ the separation preventing member 57 at the expense of the load capacity of the bearing.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a double-row tapered roller bearing that achieves compactness and cost reduction and prevents the separation of the inner ring with a simple configuration.

  In order to achieve such an object, the invention according to claim 1 of the present invention includes an outer member integrally formed with an outer rolling surface of a tapered double row on the inner periphery, and an outer side of the double row on the outer periphery. A pair of inner rings formed with a tapered inner rolling surface opposed to the rolling surface, a plurality of tapered rollers accommodated in a freely rolling manner between the both rolling surfaces via a cage, and the outer side A seal attached to an opening of an annular space formed between the member and the inner ring, and a large collar for guiding the tapered roller is formed on the larger diameter side of the inner raceway surface of the inner ring. In the back-to-back type double row tapered roller bearing set in a state where the front side end faces of each other are abutted, the seal is composed of an annular seal plate and a slinger arranged to face each other. A cylindrical portion fitted to the outer diameter of the cylindrical portion, and extends radially outward from the cylindrical portion. A cylindrical portion fitted with the inner periphery of the end portion of the outer member; a vertical plate portion extending radially inward from the cylindrical portion; and a bearing from the vertical plate portion. A cored bar having a cylindrical inner diameter portion extending inward, a side lip integrally joined to the cored bar and slidably contacted with the standing plate portion of the slinger, and slidably contacted with the cylindrical portion of the slinger The distance between the large end surface of the tapered roller and the inner diameter portion of the cored bar is set smaller than the distance between the cage and the cored bar.

  Thus, in the back-to-back type double row tapered roller bearing having the first generation or the second generation structure, the seal is composed of the annular seal plate and the slinger arranged to face each other, and the slinger is arranged outside the inner ring. A cylindrical portion fitted to the diameter, and a standing plate portion extending radially outward from the cylindrical portion, and the seal plate is fitted to the inner periphery of the end of the outer member; and the cylindrical portion A cored bar having a standing plate part extending radially inward from the cylindrical part and a cylindrical inner diameter part extending from the standing plate part to the bearing inward side, and is integrally joined to the cored bar, and is attached to the slinger standing plate part. A seal member having a side lip that is slidably contacted and a radial lip that is slidably contacted by the cylindrical portion of the slinger, and the distance between the large end surface of the tapered roller and the inner diameter portion of the core metal is such that the cage and the core metal Because it is set smaller than the distance of Even if the sub-assembly consisting of a ring, a tapered roller and a cage moves in the axial direction, the interference between the cage and the seal can be prevented with a simple configuration without adding parts such as separation preventing members or special processing. In addition, it is possible to provide a double row tapered roller bearing that is compact and low in cost.

  Preferably, as in the invention described in claim 2, the distance between the large end surface of the tapered roller and the inner diameter portion of the cored bar is set to a distance at which the radial lip does not fall off from the cylindrical portion of the slinger. Thus, it is possible to prevent the radial lip from being damaged and to secure a desired sealing property.

  Further, as in the invention according to claim 3, a locking portion that protrudes toward the inner ring side is formed at an end portion of the inner diameter portion of the core metal, and a predetermined radial clearance is provided between the inner ring and the outer diameter. If the labyrinth seal made of is configured, leakage of the lubricating grease sealed inside the bearing to the outside can be prevented without providing a grease lip, and the torque of the bearing can be reduced.

  According to a fourth aspect of the present invention, there is provided a labyrinth seal having a grease lip extending in an inward direction of the bearing on the seal member and having a predetermined radial clearance between the inner ring and the outer diameter. If this is configured, it is possible to prevent leakage of the lubricating grease sealed inside the bearing to the outside, and to achieve a reduction in torque of the bearing.

  In addition, if a garter spring is attached to the radial lip as in the invention described in claim 5, the lip tension force can be maintained at a predetermined value, and stable sealing performance can be ensured.

  The double-row tapered roller bearing according to the present invention includes an outer member in which a tapered double-row outer rolling surface is integrally formed on the inner periphery, and a tapered shape on the outer periphery facing the outer-rolling surface of the double-row. Formed between the outer member and the inner ring, a pair of inner rings on which inner rolling surfaces are formed, a plurality of tapered rollers that are rotatably accommodated between the both rolling surfaces via a cage. And a seal attached to the opening of the annular space, a large collar for guiding the tapered roller is formed on the large-diameter side of the inner raceway surface of the inner ring, and the front side end surface of the inner ring is abutted In the double-sided tapered roller bearing of the back-to-back type set in a closed state, the seal is composed of an annular seal plate and a slinger arranged to face each other, and the slinger is fitted to the outer diameter of the inner ring. A cylindrical portion and a standing plate portion extending radially outward from the cylindrical portion, A cylindrical part fitted to the inner periphery of the end of the outer member, a vertical part extending radially inward from the cylindrical part, and a cylindrical inner diameter extending from the vertical part to the bearing inward side And a seal member having a side lip that is integrally joined to the core bar and that is slidably contacted with the standing plate portion of the slinger, and a radial lip that is slidably contacted with the cylindrical portion of the slinger. In addition, since the distance between the large end surface of the tapered roller and the inner diameter portion of the cored bar is set smaller than the distance between the cage and the cored bar, the inner ring, the tapered roller and the cage during transportation, etc. Even if the sub-assembly moves in the axial direction, it is possible to prevent interference between the retainer and the seal with a simple configuration without adding parts such as a separation preventing member or special processing, and making it compact. Double row tapered roller bearing for cost reduction It is possible to provide.

  A pair of outer members in which a tapered double row outer rolling surface is integrally formed on the inner periphery and a tapered inner rolling surface facing the outer rolling surface of the double row is formed on the outer periphery. An inner ring, a plurality of tapered rollers that are rotatably accommodated between the rolling surfaces via a cage, and an opening in an annular space formed between the outer member and the inner ring are mounted. A back-to-back type compound set in a state in which a large collar for guiding the tapered roller is formed on the large-diameter side of the inner raceway surface of the inner ring, and the front end surface of the inner ring is abutted. In the row tapered roller bearing, the seal includes an annular seal plate and a slinger arranged to face each other, and the slinger is fitted to the outer diameter of the inner ring, and the cylindrical portion is radially outward from the cylindrical portion. The seal plate is disposed on the inner periphery of the end of the outer member. A cylindrical portion to be joined, a standing plate portion extending radially inward from the cylindrical portion, a cylindrical inner diameter portion extending from the standing plate portion to the bearing inward side, and an inner ring side at an end portion of the inner diameter portion And a side lip that is integrally joined to the metal core and is slidably contacted with the standing plate portion of the slinger, and a radial lip that is slidably contacted with the cylindrical portion of the slinger. And a distance between the large end surface of the tapered roller and the locking portion of the cored bar is smaller than a distance between the cage and the cored bar, and the radial lip is a cylinder of the slinger. The distance is set so that it does not fall off the part.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a first embodiment of a double row tapered roller bearing according to the present invention, and FIG. 2 is an enlarged view of a main part showing a seal portion of FIG.

  This double row tapered roller bearing 1 has a configuration called a first generation used in a wheel bearing device, and an outer ring having tapered double row outer raceway surfaces 2a and 2a formed on the inner periphery. (Outer member) 2, a pair of inner races 3 formed on the outer periphery with tapered inner rolling surfaces 3 a facing the double row outer rolling surfaces 2 a, 2 a, and the both rolling surfaces are accommodated. Double-row tapered rollers 4 and 4, a cage 5 that holds these tapered rollers 4 in a rollable manner, and seals 6 and 6 attached to both ends of the outer ring 2, and a pair of inner rings 3, 3 is a back-to-back type double-row tapered roller bearing set in a state where the front end faces of 3 are butted. The inner ring 3 is formed with a large flange 3b at the end on the large diameter side, and guides the tapered roller 4 in contact with the large end surface 4a of the tapered roller 4.

  The outer ring 2 is made of high carbon chrome bearing steel such as SUJ2 (JIS G 4805) or carburized steel. The high carbon chrome bearing steel is tempered at 820 to 860 ° C. and then tempered at 160 to 200 ° C., The core is hardened in the range of 58 to 64 HRC. In the case of carburized steel, the surface is hardened in the range of 58 to 64 HRC. On the other hand, the inner ring 3 and the tapered roller 4 are also made of high carbon chrome bearing steel such as SUJ2 (JIS G 4805) or carburized steel, like the outer ring 2, and the high carbon chrome bearing steel has a core in the range of 58 to 64 HRC. In the case of carburized steel, the surface is hardened in the range of 58 to 64 HRC.

  In this double row tapered roller bearing 1, tapered rollers 4 are assembled in advance in a cage 5, and subassemblies assembled to the inner ring 3 are fitted and inserted from both sides of the outer ring 2, respectively, from the annular space between the outer ring 2 and the inner ring 3. A predetermined amount of grease is enclosed. Thereafter, the seals 6 and 6 are attached and assembled.

  As shown in an enlarged view in FIG. 2, the seal 6 is configured by a so-called high pack seal including an annular seal plate 7 and a slinger 8 that are disposed to face each other. The seal plate 7 includes a cored bar 9 and a seal member 10 integrally joined to the cored bar 9 by vulcanization adhesion or the like. The core 9 is made of an austenitic stainless steel plate (JIS standard SUS304 type or the like), a ferritic stainless steel plate (JIS standard SUS430 type or the like), or a rust-proof cold rolled steel plate (JIS standard SPCC). A cylindrical portion 9a that is formed by press working from the system or the like, and is fitted to the inner periphery of the end portion of the outer ring 2, a vertical plate portion 9b that extends radially inward from the cylindrical portion 9a, and a vertical plate portion 9b It has a cylindrical inner diameter portion 9c extending inward of the bearing, and an engaging portion 9d protruding toward the inner ring 3 at the end of the inner diameter portion 9c. The seal member 10 is made of an elastic member such as nitrile rubber, and is integrally joined to the inner peripheral surface of the cored bar 9 and has a side lip 10a and a radial lip 10b.

  Slinger 8 can be an austenitic stainless steel plate (JIS standard SUS304 or the like), a ferritic stainless steel plate (JIS standard SUS430 or the like), or a rust-proof cold rolled steel plate (JIS standard SPCC system). Etc.) and is formed by pressing, and has a cylindrical portion 8a fitted to the outer periphery of the inner ring 3, and a standing plate portion 8b extending radially outward from the cylindrical portion 8a, and the cross section is substantially L-shaped. Is formed. The side lip 10a of the seal member 10 is in sliding contact with the upright plate portion 8b, and the radial lip 10b is in sliding contact with the cylindrical portion 8a. Further, the labyrinth seal 11 is configured such that the outer edge of the standing plate portion 8b of the slinger 8 faces the seal plate 7 through a slight radial clearance.

  Here, in this embodiment, the distance e1 between the large end surface 4a of the tapered roller 4 and the locking portion 9d of the cored bar 9 is set to a predetermined value. That is, the distance that the radial lip 10b does not fall off the cylindrical portion 8a of the slinger 8 and the cage 5 and the seal 6 do not interfere even if the sub-assembly comprising the inner ring 3, the tapered roller 4 and the cage 5 moves in the axial direction. Is set to Here, the range of e1 = 0.5 to 1.0 mm is set in consideration of the pocket clearance of the cage 5 and the manufacturing variation of each component. As a result, it is possible to prevent the inner ring 3 from being separated during transportation or the like with a simple configuration without adding parts such as a separation preventing member or special processing, thereby reducing the size and cost, and the radial lip 10b. The desired sealing property can be secured by preventing the damage.

  Further, here, the locking portion 9d of the core metal 9 is formed to protrude toward the inner ring 3, and the radial clearance e2 with the outer diameter of the inner ring 3 is set to a predetermined value (clearance 0.1 to 0.5 mm). Constitutes the labyrinth seal. Thereby, without providing a grease lip, leakage of the lubricating grease sealed inside the bearing to the outside can be prevented, and a reduction in the torque of the bearing can be achieved by eliminating the grease lip.

  FIG. 3 is a longitudinal sectional view showing a second embodiment of the double row tapered roller bearing according to the present invention, and FIG. 4 is an enlarged view of a main part showing the seal portion of FIG. In addition, the same site | part, the same component as the embodiment mentioned above, the part which has the same function, and a site | part are attached | subjected with the same code | symbol, and the overlapping description is abbreviate | omitted.

  This double-row tapered roller bearing 12 has a configuration called a second generation used in a wheel bearing device, and integrally has a wheel mounting flange 13 for mounting a wheel (not shown) on the outer periphery. The outer member 14 is formed with a tapered double row outer rolling surface 14a, 14a on the inner periphery, and the tapered inner rolling surface facing the double row outer rolling surface 14a, 14a on the outer periphery. A pair of inner rings 3, 3 formed with 3a, double-row tapered rollers 4, 4 accommodated between both rolling surfaces, and holding for holding these double-row tapered rollers 4, 4 in a freely rolling manner 5 and 5 are provided. Seals 15 and 15 are attached to seal the annular space formed between the outer member 14 and the inner ring 3, leakage of lubricating grease sealed inside the bearing, rainwater and Prevents dust from entering.

The outer member 14 is made of high carbon chrome bearing steel such as SUJ2 or carbon 0.4 such as S53C.
Made of medium-high carbon steel containing 0-0.80wt%, high-carbon chromium bearing steel is 820-860 ° C
After being tempered, the material is tempered at 160 to 200 ° C. and cured to the core in the range of 58 to 64 HRC. In the case of medium-high carbon steel, the rolling surface is hardened by induction hardening to a surface hardness of 58 to 64 HRC.

  As shown in an enlarged view in FIG. 4, the seal 15 is formed of a high pack seal including an annular seal plate 16 and a slinger 8 that are arranged to face each other. The seal plate 16 includes a metal core 17 and a seal member 18 integrally joined to the metal core 17 by vulcanization adhesion or the like. The core 17 is made of an austenitic stainless steel plate (JIS standard SUS304 or the like), a ferritic stainless steel plate (JIS standard SUS430 or the like), or a rust-proof cold rolled steel plate (JIS standard SPCC). A cylindrical portion 17a that is formed by press working from the system etc. and is fitted to the inner periphery of the end of the outer member 14, a vertical plate portion 17b that extends radially inward from the cylindrical portion 17a, and the vertical plate portion And a cylindrical inner diameter portion 17c extending inwardly from the bearing 17b.

  On the other hand, the seal member 18 is made of an elastic member such as nitrile rubber, and is integrally joined to the inner peripheral surface of the cored bar 17, and includes a side lip 18 a, a radial lip 18 b, and a grease lip 18 c extending obliquely inwardly toward the bearing. Have. The radial lip 18b is provided with a garter spring 19 that holds the lip tension force at a predetermined value, thereby ensuring a stable sealing performance. The side lip 18a is in sliding contact with the standing plate portion 8b of the slinger 8, and the radial lip 18b is in sliding contact with the cylindrical portion 8a. Further, the grease lip 18c has a radial clearance e3 with the outer diameter of the inner ring 3 set to a predetermined value (a clearance of 0 to 0.5 mm), and constitutes a labyrinth seal. As a result, the leakage of the lubricating grease enclosed in the bearing can be prevented and the torque of the bearing can be reduced.

  Here, in this embodiment, the distance e1 between the large end surface 4a of the tapered roller 4 and the inner diameter portion 17c of the cored bar 17 is set to a predetermined value. Thereby, even if the sub-assembly comprising the inner ring 3, the tapered roller 4 and the cage 5 moves in the axial direction, the radial lip 18b does not fall off from the cylindrical portion 8a of the slinger 8, and the cage 5 and the seal 15 do not interfere with each other. Set to distance. As a result, it is possible to provide a double row tapered roller bearing 12 that is compact and low in cost, and that prevents separation of the inner ring 3 with a simple configuration.

  The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

  The double-row tapered roller bearing according to the present invention can be applied to a wheel bearing device of a first generation or second generation structure that rotatably supports a wheel.

It is a longitudinal section showing a 1st embodiment of a double row tapered roller bearing concerning the present invention. It is a principal part enlarged view which shows the seal part of FIG. It is a longitudinal cross-sectional view which shows 2nd Embodiment of the double row tapered roller bearing which concerns on this invention. It is a principal part enlarged view which shows the seal part of FIG. It is a longitudinal cross-sectional view which shows the conventional double row tapered roller bearing. It is a principal part enlarged view of FIG.

Explanation of symbols

1, 12 ... Double row tapered roller bearings 2, 14 ... Outer members 2a, 14a ... Outer rolling surface 3 ...・ ・ ・ ・ ・ Inner ring 3a ・ ・ ・ ・ ・ ・ Inner rolling surface 3b ・ ・ ・ ・ ・ ・ Large pin 4 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Taper roller 4a ・································································································· Seals 7 and 16 8 ... Slinger 8a, 9a, 17a ... Cylindrical part 8b, 9b, 17b ... Standing plate part 9, 17 ... ... Core metal 9c, 17c ······· 9d inner diameter portion ··· Locking portions 10 and 18 ······ Seal members 10a and 18a ··· Side lips 10b and 18b ··· ..Radial lip 11 Seal 13 ... Wheel mounting flange 18c ... Grease lip 19 ... Garter spring 50 ...・ Double-row tapered roller bearing 51 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer ring 51a ・ ・ ・ ・ ・ ・ ・ ・ Outer rolling surface 52 ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 52a ・ ・ ・.... Inner rolling surface 53 ... Cage 54 ... Conical roller 55 ... Seal 56 ... ······································································································· Part 60 ... 2nd gap 61 ... Axle 62 ... Axle A ... ..Width C between the end face of the cage and the end face of the seal ············ D width between holding wall surfaces D ··········· Widths d1, d2 between the bent portions and the bent portion of the separation preventing member Width e1 between the wall surfaces of the holding recess e1 ... Distance e2 between the large end face of the tapered roller and the cored bar locking part ... Clearance e3 between the inner ring and the outer diameter of the inner ring e3 ··· Radial clearance between the grease lip and the outer diameter of the inner ring

Claims (5)

An outer member in which a tapered double row outer rolling surface is integrally formed on the inner periphery;
A pair of inner rings formed on the outer periphery with tapered inner rolling surfaces facing the double row outer rolling surfaces;
A plurality of tapered rollers accommodated so as to roll freely between the rolling surfaces via a cage;
A seal attached to an opening of an annular space formed between the outer member and the inner ring,
In a back-to-back double row tapered roller bearing in which a large flange for guiding the tapered roller is formed on the large-diameter side of the inner raceway surface of the inner ring, and the front-side end surface of the inner ring is set in abutment state. ,
The seal is composed of an annular seal plate and a slinger arranged to face each other,
The slinger has a cylindrical portion fitted to the outer diameter of the inner ring, and a standing plate portion extending radially outward from the cylindrical portion,
The seal plate has a cylindrical portion that is fitted to the inner periphery of the end of the outer member, a vertical plate portion that extends radially inward from the cylindrical portion, and a cylindrical shape that extends from the vertical plate portion to the bearing inward side. A cored bar having an inner diameter part of
A seal member having a side lip slidably contacted with the standing plate portion of the slinger, and a radial lip slidably contacted with the cylindrical portion of the slinger,
A double-row tapered roller bearing, wherein a distance between a large end surface of the tapered roller and an inner diameter portion of the cored bar is set to be smaller than a distance between the cage and the cored bar.   2. The double-row tapered roller bearing according to claim 1, wherein the distance between the large end surface of the tapered roller and the inner diameter portion of the cored bar is set to a distance at which the radial lip does not fall off from the cylindrical portion of the slinger.   The locking part which protrudes to the said inner ring | wheel side is formed in the edge part of the internal diameter part of the said metal core, The labyrinth seal which consists of predetermined | prescribed radial clearance between the said outer ring | wheels is comprised. 2. Double-row tapered roller bearing according to 2.   The grease lip which inclines and extends in the bearing inward side is formed in the seal member, and a labyrinth seal having a predetermined radial clearance is formed between the outer ring and the outer diameter of the inner ring. Double row tapered roller bearing.   The double row tapered roller bearing according to any one of claims 1 to 4, wherein a garter spring is attached to the radial lip.

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