JP4554471B2 - Double row tapered roller bearings for wheels - Google Patents

Description

  The present invention relates to a double-row tapered roller bearing for a wheel that rotatably supports a wheel of a truck or the like with respect to a suspension device.

  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. A double-row angular contact ball bearing having a large bearing rigidity, exhibiting durability against misalignment, and having a small rotational torque is often used from the viewpoint of improving fuel efficiency. On the other hand, double-row tapered roller bearings are used in vehicles such as trucks and off-road cars that have a heavy vehicle body weight. This double row tapered roller bearing has a large load capacity and is suitable for carrying a radial load, an axial load, and a combined load thereof.

  An example of a conventional wheel bearing device using a double-row tapered roller bearing is shown in FIG. The wheel bearing device includes an outer ring 51 having a tapered double row outer rolling surface 51a, 51a formed on the inner periphery, and a tapered inner surface facing the double row outer rolling surface 51a, 51a on the outer periphery. A pair of inner rings 52, 52 formed with a rolling surface 52 a, a double row tapered roller 54 accommodated between both rolling surfaces via a cage 53, and both ends of the outer ring 51. A double-row tapered roller bearing 57 including the sealed seals 55 and 56 is provided.

  Here, a pair of inner rings 52, 52 of the double row tapered roller bearing 57 are fitted and inserted into a stepped portion 58 a formed at the shaft end of the axle 58. These inner rings 52, 52 are fastened and fixed by a fixing nut 59, and a wheel hub 60 is attached with a hub bolt 61 to an outward flange 51 b provided integrally with the rotatable outer ring 51.

The double row tapered roller bearing 57 supports a wheel (not shown) in rotation, supports a heavy vehicle weight, and also receives a moment load. Therefore, the stepped portion 58a in the inner ring 52 and the axle 58 is inserted. There is a possibility that seizure occurs due to a minute slip between the outer diameter surfaces of the two and the two adhere to each other. As described above, when the fitting surface is fixed, there is a problem that it is difficult to remove and attach the bearing during maintenance or replacement of parts. Therefore, in order to solve such a problem, in the wheel bearing device in which the wheel is rotatably supported on the axle 58 by the double row tapered roller bearing 57, phosphoric acid is formed on the inner diameter surface of the inner ring 52 of the double row tapered roller bearing 57. A lubricating film 62 made of a salt film or the like is formed. That is, by forming the lubricating film 62 on the inner diameter surface of the inner ring 52, even if a slip occurs between the stepped portion 58 a and the fitting surface of the inner ring 52, these fitting surfaces are prevented from seizing. .
JP 2001-99175 A

  In such a conventional wheel bearing device, the lubricating film 62 is formed on the inner diameter surface of the inner ring 52 in the double row tapered roller bearing 57, so that even if a slip occurs between the fitting insertion surfaces of the axle 58 and the inner ring 52, it will burn. The inner ring 52 in the double row tapered roller bearing 57 of this type is usually press-fitted and fixed to the axle 58 in order to prevent creep. Therefore, when disassembling and reassembling during periodic inspections and repairs at a dealer, a large load is required when the inner ring 52 is pulled out of the axle 58 and re-pressed, and a large press or large dedicated jig is required. It was. This was one of the factors that hindered workability during maintenance, inspection and repair. Here, creep refers to a phenomenon in which the fitting surface is a mirror surface, a cloudy surface, or a galling due to insufficient fitting or poor accuracy of the fitting surface.

  Further, in such a wheel bearing device, the outer ring 51 of the double row tapered roller bearing 57 rotates. Therefore, the press-fitting squeeze of the inner ring 52 with respect to the axle 58 is relatively small compared to the structure in which the inner ring 52 rotates. When the inner ring 52 is press-fitted into the axle 58, the lubricating film 62 may be peeled off, and an improvement in durability has been desired.

  The present invention has been made in view of such conventional problems, and provides a double-row tapered roller bearing for a wheel that has reduced drawing / press-fit loads and improved workability during maintenance and inspection. Objective.

In order to achieve such an object, the invention according to claim 1 of the present invention is an outer member in which a tapered double row outer rolling surface is formed on the inner periphery, and the outer member is inserted into the outer member. A pair of inner rings each having an inner rolling surface opposed to the outer rolling surface of the double row on the outer periphery, and a double row of cones rotatably accommodated between the rolling surfaces via a cage A double-row tapered roller bearing for a wheel comprising a roller and seals attached to both ends of the outer member, and set in a state where the front side end surfaces of the pair of inner rings are abutted to constitute a back-to-back type in, with the outer member is a bearing ring on the rotating side, the inner periphery of the inner ring, in order to reduce the area of the mating surface in the inner ring, the axial direction with a level difference with respect to the fitting surface Extending from the axial position substantially the same as the small-diameter end of the inner rolling surface of the inner ring. A large-diameter step portion is formed in the no-load region extending over the side end surface, and an annular mounting groove is formed in the region of the large-diameter step portion, and the end ring having a substantially U-shaped cross section in the mounting groove The end of the connecting ring consisting of is locked.

In this way, in the double-row tapered roller bearing for the wheel that constitutes the back-to-back type and supports the wheel rotatably, the outer member is a raceway on the rotation side, and the inner ring is connected to the inner ring of the inner ring. in order to reduce the area of the mating face, extending to the fitting surface in the axial direction with a step, ranging from substantially the same axial position as the smaller diameter end of the inner raceway surface on the front end face of the inner ring in the inner ring A large-diameter step portion is formed in the no-load region, and an annular mounting groove is formed in the region of the large-diameter step portion, and a connecting ring comprising an end ring having a substantially U-shaped cross section in the mounting groove. Since the end of the inner ring is locked, the area of the fitting surface of the inner ring can be reduced without affecting the load, and the load when the inner ring is pulled out from the axle and re-pressed can be reduced. Can be reduced, using large presses and large dedicated jigs. It can easily desorb the bearing without. Therefore, it is possible to provide a double-row tapered roller bearing for a wheel that further improves workability during maintenance / inspection and repair.

Preferably, as in the invention described in claim 2, the outer member is a rotating raceway and integrally has a wheel attachment flange for attaching a wheel hub to the outer periphery of the outer side. Also good.

Further, the invention according to claim 3, with the outer member is formed in a substantially cylindrical shape which is fitted over a predetermined Interference the knuckle, the outer periphery of the outer member, in the outer member in order to reduce the area of the mating surface, the mating surfaces relative to cylindrical portion extending in the axial direction with a step is formed, the cylindrical portion is formed in the no-load region over the axial direction Therefore, the area of the fitting surface of the outer member can be reduced without affecting the load, and the load when the outer member is pulled out from the knuckle and re-pressed can be reduced. .

Preferably, as in the invention of claim 4, wherein the cylindrical portion is from said substantially same axial position as one of the smaller diameter end of the outer raceway run surfaces of the double row other smaller diameter end and substantially If it is formed over the same axial direction position, the range of the small-diameter stepped portion becomes a no-load region, so that it does not affect the load application.

More preferably, as in the invention described in claim 5, the small-diameter step portion is formed from the substantially same axial position as the large-diameter side end portion of the outer rolling surface over the end surface of the outer member. If it is done, the area of the fitting surface of the outer member can be effectively reduced, and the load when pulling out and re-pressing can be further reduced.

The double-row tapered roller bearing for a wheel according to the present invention includes an outer member having a tapered double-row outer raceway formed on the inner periphery, and is inserted into the outer member. A pair of inner rings formed with an inner rolling surface facing the outer rolling surface, a double row tapered roller accommodated between the both rolling surfaces via a cage, and the outer member; of a both ends attached to the seal, in the pair of inner rings of the wheel for double row tapered roller bearing is set in a state where the front end face is butted constituting the rear mating type, before Symbol annulus the inner circumference, in order to reduce the area of the mating surface in the inner ring, extends to the fitting surface in the axial direction with a step, substantially the same axial position as the smaller diameter end of the inner raceway surface of the inner ring A large-diameter step portion is formed in a no-load region extending from the front side end surface of the inner ring to the large-diameter step. The annular mounting groove in the region is formed, the end portion of the connecting ring section in the mounting groove consists shaped having ends rings approximately U is engaged, the effect in terms of a load It is possible to reduce the area of the inner ring mating surface without affecting the load, and to reduce the load when the inner ring is pulled out of the axle and re-pressed, without using a large press or large dedicated jig. However, the bearing can be easily detached. Therefore, it is possible to provide a double-row tapered roller bearing for a wheel that further improves workability during maintenance / inspection and repair.

An outer member having a tapered double row outer rolling surface formed on the inner periphery, and an inner rolling surface that is inserted into the outer member and faces the outer rolling surface of the double row are formed on the outer periphery. A pair of inner rings, a double-row tapered roller that is rotatably accommodated between both rolling surfaces via a cage, and seals attached to both ends of the outer member, In a double-row tapered roller bearing for a wheel that is set in a state where the front side end surfaces of a pair of inner rings are abutted to constitute a back-to-back type, the outer member is attached to a wheel for attaching a wheel hub to the outer periphery of the outer side and has a flange integrally on the inner periphery of the inner ring, in order to reduce the area of the mating surface in the inner ring, extends in the axial direction with a level difference with respect to the fitting surface, the inner raceway surface of the inner ring Front end of the inner ring from substantially the same axial position as the small diameter end A large-diameter step portion is formed in the no-load region, and an annular mounting groove is formed in the region of the large-diameter step portion, and the mounting groove is formed of a ring having a substantially U-shaped cross section. The end of the connecting ring is locked.

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 wheel bearing device incorporating a double row tapered roller bearing according to the present invention, and FIG. 2 is a longitudinal sectional view showing a first embodiment of the double row tapered roller bearing. . In the following description, the side closer to the outer side of the vehicle in a state assembled to the vehicle is referred to as the outer side (left side in the drawing), and the side closer to the center is referred to as the inner side (right side in the drawing).

  This wheel bearing device is for a driven wheel and includes a double-row tapered roller bearing 1 having a configuration called a second generation. The double-row tapered roller bearing 1 is fitted to a small-diameter fitting portion 3 formed at an end portion of the axle 2 via a predetermined shimiro, and is sandwiched between a shoulder portion 2 a of the axle 2 and a washer 4. These are fastened by a fixing nut 5. The double row tapered roller bearing 1 includes an outer member (outer ring) 8 integrally having a wheel mounting flange 7 for attaching a wheel hub 6 to the outer periphery on the outer side, a pair of inner rings 9, 9, and a double row tapered roller. 10 and 10.

  A plurality of bolt holes 7 a are formed at equal circumferences of the wheel mounting flange 7, and the wheel hub 6 is fastened by the hub bolt 11. Further, a cap 12 is attached to the outer side end surface of the outer member 8 via a fixing bolt 13, and the opening on the outer side of the double row tapered roller bearing 1 is closed to allow rainwater, dust, etc. to enter the bearing from the outside. Preventing intrusion.

  As shown in an enlarged view in FIG. 2, the double-row tapered roller bearing 1 has tapered double-row outer rolling surfaces 8 a and 8 a formed on the inner periphery of the outer member 8, and the outer sides of these double-rows. Tapered inner rolling surfaces 9a facing the rolling surfaces 8a and 8a are formed on the outer circumference of the inner ring 9, respectively. The double-row tapered rollers 10 and 10 are movably accommodated between the rolling surfaces 8a and 9a via the cage 14, and are formed at the large-diameter end portions of the pair of inner rings 9 and 9. The tapered roller 10 is guided by the large collar 9b. The double row tapered roller bearing 1 is set in a state where the front side (small diameter side) end faces of the pair of inner rings 9 and 9 are abutted, and constitutes a so-called back-to-back type.

  The outer member 8 is formed of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 8a and 8a have a surface in the range of 58 to 64HRC by induction hardening. It has been cured. Further, the inner ring 9 and the tapered roller 10 are made of high carbon chrome steel such as SUJ2 or carburized steel, and the high carbon chrome steel is hardened in the range of 58 to 64 HRC to the core part by quenching. The surface is cured in the range of 58 to 64 HRC.

  Seals 15 and 16 are attached to both ends of the outer member 8 to seal the opening of the annular space formed between the outer member 8 and the inner ring 9. The seals 15 and 16 prevent the lubricating grease enclosed in the bearing from leaking to the outside and preventing rainwater, dust, and the like from entering the bearing from the outside.

  Out of the seals 15 and 16, the outer seal 15 is constituted by a simple labyrinth type seal because rain or dust does not enter the bearing directly from the outside by the cap 12 (see FIG. 1). Has been. Specifically, the seal 15 has a substantially L-shaped cross section formed by pressing from a steel plate, and an inner edge of the seal 15 faces the outer diameter of the inner ring 9 via a slight radial clearance.

  On the other hand, since the inner seal 16 is directly exposed to the outside, the inner seal 16 is composed of a composite seal having a strong sealing property. That is, it consists of a seal plate 17 fitted in the outer member 8 and a slinger 18 fitted in the inner ring 9 and formed into a substantially L-shaped section by pressing from a steel plate having corrosion resistance such as a stainless steel plate. Are arranged opposite to each other. The seal plate 17 includes a core metal 19 having a substantially L-shaped cross section formed by press working from a corrosion-resistant steel plate, and a side lip 20a that is integrally vulcanized and bonded to the core metal 19 and slidably contacts the slinger 18, and a fork. It has the sealing member 20 which consists of the shape-like radial lips 20b and 20c.

  A connecting ring 21 is attached to the small-diameter side ends of the pair of inner rings 9, which face each other. The connection ring 21 is formed by pressing a steel plate into a substantially U-shaped cross section as an end ring, and an end of the connection ring 21 is formed in an annular mounting groove 22 formed on the inner periphery of the small diameter end of the inner ring 9. The pair of inner rings 9 are engaged with each other with a predetermined pulling strength. The connecting ring 21 prevents the pair of inner rings 9, 9 from being separated and facilitates handling. When the pair of inner rings 9, 9 is pulled out from the axle 2, the outer ring 9 is pulled out to remove the axle. 2, the inner ring 9 on the inner side which is to remain on can be easily removed, and the work of attaching and detaching the bearing to the axle 2 can be simplified.

  Here, in this embodiment, a large-diameter step portion 23 extending in a predetermined range in the axial direction is formed on the inner circumference of the inner ring 9 fitted to the axle 2 with a slight step with respect to the fitting surface 9c. Yes. The large diameter step portion 23 is formed from the position corresponding to the small diameter side end portion of the inner rolling surface 9a (shown by a broken line in the drawing) to the front side end surface. Since the range of the large-diameter step portion 23 is a no-load region, there is no influence in applying a load, and the area of the fitting surface 9c in the inner ring 9 can be reduced. That is, by forming the large-diameter step 23 on the inner periphery of the inner ring 9, the load when the inner ring 9 is pulled out from the axle 2 and re-pressed can be substantially reduced by 20 to 40% compared to the conventional case. It becomes possible, and the bearing can be easily detached without using a large press or a large dedicated jig. Therefore, it is possible to provide the double-row tapered roller bearing 1 for a wheel that further improves workability during maintenance / inspection and repair.

  FIG. 3 is a longitudinal sectional view showing another wheel bearing device in which the double row tapered roller bearing according to the present invention is incorporated, and FIG. 4 is a longitudinal sectional view showing a second embodiment of the double row tapered roller bearing for the wheel. FIG. In addition, the same code | symbol is attached | subjected to the component same site | part or the site | part which has the same function as embodiment mentioned above, and detailed description is abbreviate | omitted.

  This wheel bearing device is for a drive wheel and includes a double-row tapered roller bearing 24 having a configuration called a first generation. The double-row tapered roller bearing 24 is fitted to a cylindrical fitting step 25a formed on the hub wheel 25 and a knuckle 26 via a predetermined shimiro, and is connected to an outer joint member 28 of the constant velocity universal joint 27. In a state of being clamped by the hub wheel 24, it is tightened by the fixing nut 5. The hub wheel 25 integrally has a wheel mounting flange 7 for mounting the wheel hub 6 and the brake rotor 29 at an end portion on the outer side, and a plurality of hub bolts 11 are planted around the circumference of the wheel mounting flange 7. It is installed. A serration (or spline) 25 b is formed on the inner periphery of the hub wheel 25, and a serration (or spline) 30 a that engages with the serration 25 b is engraved on the outer periphery of the stem portion 30 of the outer joint member 28. ing. The stem portion 30 is fitted into the hub wheel 25, and the hub wheel 25 and the outer joint member 28 are coupled so as to be able to transmit torque and to be separated in the axial direction.

  As shown in an enlarged view in FIG. 4, the double row tapered roller bearing 24 includes an outer member (outer ring) 31 having a tapered double row outer raceway surfaces 8 a and 8 a formed on the inner periphery, and a double row of double row tapered roller bearings 24. A pair of inner races 9 each having a tapered inner raceway surface 9a facing the outer raceway surfaces 8a, 8a are formed, and the two raceway surfaces 8a, 9a are accommodated in a freely rollable manner via a retainer 14. The double-row tapered rollers 10 and 10, seals 15 and 16 attached to both ends of the outer member 31, and a connecting ring 21 attached to the small-diameter end of the inner ring 9 are provided. The outer member 31 is made of high carbon chrome steel such as SUJ2 or carburized steel, and the high carbon chrome steel is hardened in the range of 58 to 64 HRC up to the core portion by quenching. In the case of carburized steel, the surface is 58 to 64 HRC. It has been cured to the extent of.

  Here, in this embodiment, the inner ring 9 fitted to the hub wheel 25 has a large step extending in a predetermined range in the axial direction with a slight step with respect to the fitting surface 9c as in the above-described embodiment. A diameter step portion 23 is formed. Furthermore, small diameter step portions 32 and 33 extending in a predetermined range in the axial direction are formed on the outer periphery of the outer member 31 with a slight step with respect to the fitting surface 31a with the knuckle 26 (see FIG. 3). The small-diameter step portion 32 is a central portion in the axial direction of the outer periphery, and from the position corresponding to one small-diameter side end of the double row outer rolling surfaces 8a, 8a (shown by a broken line in the figure), It is formed over the position corresponding to the part. Further, the small-diameter step portion 33 is formed from the position corresponding to the large-diameter side end portion of the outer rolling surface 8a (indicated by a broken line in the figure) from the outer periphery of the end portion of the outer member 31 to the end surface. Yes. Since the range of this small diameter step part 32 and 33 becomes a no-load area | region, it does not have influence in loading a load, and can reduce the fitting surface 31a of the outward member 31. FIG. That is, by forming the small-diameter stepped portions 32 and 33 on the outer periphery of the outer member 8, the load when the outer member 8 is pulled out from the knuckle (not shown) 26 and re-pressed is substantially larger than in the conventional case. Therefore, the bearing can be easily attached and detached in combination with the large-diameter step portion 23 of the inner ring 9. Therefore, workability at the time of maintenance / inspection and repair can be further improved.

  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 for a wheel according to the present invention can be applied to the first and second generation wheel bearing devices for rotatably supporting the wheel regardless of the driven wheel side or the drive wheel side.

It is a longitudinal cross-sectional view which shows the bearing apparatus for wheels in which the double row tapered roller bearing which concerns on this invention was integrated. It is a longitudinal cross-sectional view which shows 1st Embodiment of a double row tapered roller bearing same as the above. It is a longitudinal cross-sectional view which shows the other bearing apparatus for wheels in which the double row tapered roller bearing which concerns on this invention was integrated. It is a longitudinal cross-sectional view which shows 2nd Embodiment of a double row tapered roller bearing same as the above. It is a longitudinal cross-sectional view which shows the wheel bearing apparatus in which the conventional double row tapered roller bearing was integrated.

Explanation of symbols

1, 24... Double row tapered roller bearing 2... Axle 2a... Shoulder 3. ···································································· Wheel hub 7 ········· Bolt holes 8, 31 ··· Outer member 8a ··· Outer rolling surface 9 ······ Inner ring 9a ··· ... Inner rolling surface 9b ......... Large 9c, 31a ... Fitting surface 10 ... Taper roller 11 ... Hub bolt 12 ... Cap 13 ... Fixing bolt 14 ... Retainer 15, 16 ... Seal 17 ... Seal Board 18 ... Slinger 19 ... Gold 20 ... Seal member 20a ... Side lip 20b, 20c ... Radial lip 21 ... Connection ring 22 ... Mounting groove 23... Large diameter step 25... Hub wheel 25 a... Fitting step 25 b, 30 a. ··· Knuckle 27 ··· Constant velocity universal joint 28 ··· Outer joint member 29 · · · Brake rotor 30 ··· Stem portion 32, 33 ... Small diameter step portion 51 ... Outer ring 51a ... Outer rolling surface 51b ... Flange 52 ... ... Inner ring 52a ... Inner rolling surface 53 ... Retainer 54 ... Conical rollers 55, 56 ... Seal 5 ... Double-row tapered roller bearing 58 ... Axle 58a ... Step part 59 ... Fixing nut 60 ... ... Wheel hub 61 ... Hub bolt 62 ... Lubrication film

Claims (5)

An outer member having a tapered double row outer raceway formed on the inner circumference;
A pair of inner rings inserted into the outer member and formed with an inner rolling surface facing the outer rolling surface of the double row on the outer periphery;
A double-row tapered roller accommodated in a freely rollable manner between the rolling surfaces via a cage;
A seal mounted on both ends of the outer member;
In the double-row tapered roller bearing for a wheel, which is set in a state where the front side end faces of the pair of inner rings are butted together and constitutes a back-to-back type,
The inner circumference of the front Symbol annulus, in order to reduce the area of the mating surface in the inner ring, extends in the axial direction with a level difference with respect to the fitting surface, and a smaller diameter end of the inner raceway surface of the inner ring A large-diameter step portion is formed in a no-load region extending from substantially the same axial position to the front end surface of the inner ring, and an annular mounting groove is formed in the region of the large-diameter step portion. A double-row tapered roller bearing for a wheel, characterized in that an end portion of a connecting ring formed of a substantially U-shaped end ring is locked . 2. The double-row tapered roller bearing for a wheel according to claim 1, wherein the outer member is a rotating raceway and has a wheel mounting flange for mounting a wheel hub on the outer periphery of the outer side. In order to reduce the area of the fitting surface of the outer member on the outer periphery of the outer member, the outer member is formed into a substantially cylindrical shape that is fitted to a knuckle through a predetermined shimoshiro. the cylindrical portion extending mating surface axially with a step with respect to is formed, wheel double row tapered according to claim 1, the cylindrical portion is formed in the no-load region over the axial direction Roller bearing. Claims wherein the cylindrical portion has substantially formed over the same axial location substantially the same axial position as the other smaller diameter end and the smaller diameter end of one of the outer raceway run surfaces of the double row The double-row tapered roller bearing for a wheel according to 3. 5. The double row for a wheel according to claim 3, wherein the small-diameter step portion is formed over the end surface of the outer member from substantially the same axial position as the large-diameter side end portion of the outer rolling surface. Tapered roller bearing.

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