JP2007218292A - Bearing apparatus for wheel - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing apparatus for a wheel, which secures the durability of a bearing, and also reduces a turning torque. <P>SOLUTION: In the bearing apparatus for the wheel, a double row taper roller bearing 1 comprises: an outer member 3 which has a hub flange 3b integratedly formed on one end portion of its outer periphery so as to mount a hub, and also has a tapered double row outer rolling surface 3a formed on its inner peripheral surface; a pair of inner races 2 having a tapered inner rolling surface 2a formed on the outer periphery so as to be opposed to the double row outer rolling surface 3a; and double row taper rollers 4 retained between both rolling surfaces so as to roll. A large flange 2b for guiding the taper rollers 4 is formed on the large-diameter side of the inner rolling surface 2a. An annular recess 2d is also formed at the corner portion formed by the large flange 2b and the inner rolling surface 2a, The taper rollers 4 have a large-diameter projection 4b formed at its large-diameter side end portion. The large-diameter projection 4b is retained in the recess 2d. The contact point P of the large flange 2b and the large end surface 4a of the taper roller 4 is arranged on the extension line of the generating line of the inner rolling surface 2a. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a wheel bearing device for rotatably supporting a wheel of an automobile or the like, and more particularly to a wheel bearing device for rotatably supporting a wheel with a double row tapered roller bearing.

  In vehicles such as trucks, in recent years, the horsepower and loading capacity of vehicles have increased, and accordingly, wheel bearing devices are required to withstand the temperature rise during high loads and high speeds. A double row tapered roller bearing suitable for receiving a radial load, a thrust load, and a combined load thereof is generally used for a bearing portion of a wheel bearing device in such a vehicle.

  An example of a wheel bearing device using such a double-row tapered roller bearing is shown in FIG. This wheel bearing device is mounted on an axle for a driven wheel such as a truck and rotatably supports a wheel (not shown). In this wheel bearing device, a pair of inner rings 53 and 53 of a double-row tapered roller bearing 52 are fitted to an axle 51, and a hub 56 for attaching a wheel to an outward flange 55 provided at one end of an outer ring 54; The brake rotor 57 is fixed by bolts 58. The pair of inner rings 53, 53 are prevented from coming off by nuts 59, and wheel mounting bolts 60 for fastening the wheels are implanted in the hub 56.

  Tapered double row outer rolling surfaces 54a, 54a are formed on the inner circumference of the outer ring 54, and the outer circumferences of the pair of inner rings 53, 53 are opposed to the outer rolling surfaces 54a, 54a of the double row. Inner rolling surfaces 53a and 53a are formed respectively. Double-row tapered rollers 61, 61 are accommodated between the rolling surfaces so as to roll freely. These tapered rollers 61, 61 roll with their large end surfaces 61a abutting against large flanges 53b provided on the large diameter side of the inner rolling surface 53a of the inner ring 53. Further, seals 62 and 63 are attached to both ends of the outer ring 54 to prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater, dust and the like into the bearing from the outside.

The inner ring 53 and the tapered roller 61 are made of case-hardened steel SCr435, and as shown in FIG. 6 (b), the surface has a carbon content of 0.80% by weight or more, a Rockwell hardness of 58HRC or more, and remains. Carbonitriding layers 53c and 61b having an austenite amount of 25 to 35% by volume are formed. Moreover, the outer ring | wheel 54 is formed with medium carbon steel S53C, and the surface of the double row outer side rolling surfaces 54a and 54a is hardened by induction hardening. With such a configuration, the mechanical properties and fatigue characteristics of these parts can be improved, and the surface layer of the parts can be kept stable with a material having appropriate toughness, and the durability life under high loads and high speeds can be significantly improved. it can.
JP 2000-186721 A

  In such a conventional wheel bearing device, the double-row tapered roller bearing 52 rolls with the large end surface 61a of the tapered roller 61 coming into contact with the large flange 53b of the inner ring 53, so that the large end surface 61a and the large flange 53b While generating heat at the sliding portion to increase the temperature, it becomes a factor to increase the rotational torque of the bearing. When this rotational torque increases, fuel consumption increases, which is not preferable in terms of resource saving and environment. Moreover, since the contact pressure between the large end surface 61a and the large collar 53b increases as the load load increases, the rotational torque further increases.

  Of the rotational torque of the double row tapered roller bearing 52, the sliding torque T due to the sliding resistance between the large end surface 61a and the large flange 53b is the contact point between the large flange 53b of the inner ring 53 and the large end surface 61a of the tapered roller 61. It is said to change with position. That is, the sliding torque T is directly proportional to the contact distance e shown in FIG. 6C and is represented by T = e × f (x). Here, e indicates the distance between the extended line of the bus of the inner raceway surface 53a of the inner ring 53 and the contact point between the large collar 53b of the inner ring 53 and the large end surface 61a of the tapered roller 61, and f (x ) Indicates a function depending on conditions such as load and rotational speed, bearing internal accuracy, and the like.

  As can be seen from this general formula, the rotational torque of the bearing decreases as the contact distance e is set smaller. Usually, the grinding ring 64 of the inner ring 53 and the chamfer 61b of the tapered roller 61 are secured within a predetermined range. The contact distance e is set as small as possible. However, if it is set too small, the contact distance e is applied to the edge due to dimensional variation of each part and there is a risk of seizing due to excessive surface pressure. Therefore, in such a double row tapered roller bearing 52, the rotational torque is reduced. There was a limit.

  The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a wheel bearing device in which the durability of the bearing is ensured and the rotational torque is reduced.

  In order to achieve such an object, the invention according to claim 1 of the present invention is a wheel bearing device for rotatably supporting a wheel by a double row tapered roller bearing, wherein the double row tapered roller bearing comprises an inner An outer member having a tapered double row outer raceway formed on the circumference and at least one inner ring fitted to an axle or a hub wheel integrally having a wheel mounting flange at one end thereof, An inner member in which a tapered double-row inner rolling surface facing the double-row outer rolling surface is formed, and a double row accommodated between the both rolling surfaces via a cage so as to roll freely. In the wheel bearing device including the tapered roller, a large collar for guiding the tapered roller is formed on the large diameter side of the rolling surface of the outer member or the inner member, and the large collar and the tapered roller The contact point with the large end face is located on the extension of the bus bar of the rolling surface. It was adopted configuration.

  Thus, a wheel bearing device for rotatably supporting a wheel with a double-row tapered roller bearing, wherein the double-row tapered roller bearing has an outer periphery formed with a tapered double-row outer raceway. And at least one inner ring that is press-fitted through a predetermined shimoshiro to a hub wheel integrally having a wheel mounting flange at one end or an axle, and has a tapered shape facing the double-row outer rolling surface on the outer periphery. 1st to 3rd generation structure comprising an inner member in which a double row inner raceway is formed and a double row tapered roller accommodated between both raceway surfaces via a cage. In this wheel bearing device, a large flange is formed to guide the tapered roller on the large diameter side of the rolling surface of the outer member or the inner member, and the contact point between the large flange and the large end surface of the tapered roller is the rolling contact. Since it is arranged on the extended line of the bus on the running surface, it is used for double row tapered roller bearings. The contact distance between the tapered roller and the large cup is virtually zero, and the contact is applied to the edge to prevent seizure due to excessive surface pressure. It can theoretically be zero. Therefore, it is possible to provide a wheel bearing device in which the durability of the bearing is ensured and the rotational torque is reduced.

  Preferably, as in the invention described in claim 2, an annular large-diameter convex portion is formed at the large-diameter side end of the tapered roller, and an annular steal is formed on the large-diameter side of the rolling surface. And if the said large diameter convex part is accommodated in this steal, contact with a tapered roller and a rolling surface will not be inhibited, but desired durability can be ensured.

  Further, as in the invention according to claim 3, the inner member integrally has a wheel mounting flange at one end, and one inner rolling surface facing the double row outer rolling surface on the outer periphery. A hub wheel in which the small-diameter step portion is formed from the inner rolling surface, and the other inner rolling surface that is press-fitted into the small-diameter step portion of the hub wheel and faces the outer surface of the double row on the outer periphery. The inner member may be formed of a pair of inner rings as in the fourth aspect of the present invention.

  In addition, as in the invention described in claim 5, annular grooves are formed in the inner periphery of the front side end portions which are the butting portions of the pair of inner rings, and a connecting ring having a substantially U-shaped cross section is attached to these annular grooves. If so, the pair of inner rings are firmly integrated without any looseness, and the workability of disassembly / assembly can be simplified. In addition, since a pair of inner rings press-fitted and fixed to the axle or the like can be integrally removed during repair or the like, there is no problem that only the inner-side inner ring remains on the axle.

  A wheel bearing device according to the present invention is a wheel bearing device for rotatably supporting a wheel by a double-row tapered roller bearing, wherein the double-row tapered roller bearing has a double-row tapered outer roller. It comprises an outer member formed with a running surface and at least one inner ring fitted to an axle or a hub wheel integrally having a wheel mounting flange at one end thereof, and is opposed to the outer rolling surface of the double row on the outer periphery. A wheel bearing comprising: an inner member in which a tapered double-row inner rolling surface is formed; and a double-row tapered roller housed between the both rolling surfaces via a cage. In the apparatus, a large flange for guiding the tapered roller is formed on the large diameter side of the rolling surface of the outer member or the inner member, and a contact point between the large flange and the large end surface of the tapered roller is the rolling contact. Since it is arranged on the extended line of the bus on the running surface, it is suitable for double row tapered roller bearings. The contact distance between the tapered roller and the large hook becomes substantially zero, and the contact is applied to the edge to prevent the occurrence of seizure due to excessive surface pressure and the rotational torque due to the sliding between the large flange and the large end face. It can theoretically be zero. Therefore, it is possible to provide a wheel bearing device in which the durability of the bearing is ensured and the rotational torque is reduced.

  A wheel bearing device for rotatably supporting a wheel by a double-row tapered roller bearing, wherein the double-row tapered roller bearing is integrally formed with a hub flange for attaching a hub to one end portion of the outer periphery. A pair of outer members on which tapered double-row outer rolling surfaces are formed, and a pair of outer members fitted on the axles and formed on the outer periphery with tapered inner rolling surfaces facing the double-row outer rolling surfaces. In the wheel bearing device comprising an inner member made of an inner ring and a double row tapered roller that is rotatably accommodated between both the rolling surfaces via a cage, the inner rolling surface of the inner ring A large ridge that guides the tapered roller to the large-diameter side of the roller, and an annular steal formed at the corner between the large ridge and the inner rolling surface, and a predetermined length at the large-diameter side end of the tapered roller A large-diameter convex portion is formed, and the large-diameter convex portion is accommodated in the steal, Pancreatic contact point between the large end face of the roller is disposed on an extension line of the generatrix of the inner raceway surface.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
Fig.1 (a) is a longitudinal cross-sectional view which shows the double row tapered roller bearing in 1st Embodiment of the wheel bearing apparatus based on this invention, (b) is a principal part enlarged view of (a). 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 mounted on an axle (not shown) for a driven wheel and rotatably supports a wheel (not shown). As shown in FIG. 1 (a), a double row tapered roller bearing 1 constituting the wheel bearing device includes a pair of inner rings 2 and 2 fitted on an axle and a hub (not shown) on one end of the outer periphery. Are provided with an outer ring (outer member) 3 integrally formed with a hub flange 3b, and double row tapered rollers 4 and 4 accommodated between the inner ring 2 and the outer ring 3. Then, a bolt (not shown) is fastened to the internal thread 3c formed at the circumferentially equidistant position of the hub flange 3b, and the hub and the brake rotor to which the wheel is attached are fixed to the hub flange 3b.

  Tapered double row outer rolling surfaces 3a, 3a are formed on the inner circumference of the outer ring 3, and the outer circumferences of the pair of inner rings 2, 2 are opposed to the outer rolling surfaces 3a, 3a of the double row. Tapered inner rolling surfaces 2a and 2a are formed respectively. And the double row tapered rollers 4 and 4 are accommodated between the rolling surfaces via the cages 5 and 5 so as to roll freely. Further, a large collar 2b for guiding the tapered roller 4 is formed on the large diameter side of the inner raceway 2a of the pair of inner rings 2, 2, and a small collar 2c for preventing the tapered roller 4 from dropping off is formed on the small diameter side. Is formed. And it sets in the state in which the end surface (front side end surface) by the side of a gavel 2c was faced | matched, and comprises the double row tapered roller bearing called the 2nd generation of what is called a back-to-back type. Seals 6 and 7 are attached to both ends of the outer ring 3 to prevent leakage of lubricating grease sealed inside the bearing and intrusion of rainwater, dust, etc. into the bearing from the outside.

  The inner ring 2 and the tapered roller 4 are made of high carbon chrome bearing steel such as SUJ2, and are hardened in the range of 58 to 64 HRC up to the core by quenching. The outer ring 3 is made 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 3a and 3a have a surface hardness in the range of 58 to 64HRC by induction hardening. Has been cured.

  An annular groove 8 is formed in the inner periphery of the end portion on the side of the small collar 2c, which is a butting portion between the pair of inner rings 2, 2, and a connecting ring 9 having a substantially U-shaped cross section is mounted in the annular groove 8. The connecting ring 9 is formed by pressing a steel plate and the surface thereof is hardened. Examples of the steel plate include a carbon tool steel plate such as SK5, a stainless steel plate such as SUS304, a cold rolled steel plate such as SPCC, and the like. By elastically deforming the connecting ring 9 and mounting it in the annular groove 8, the pair of inner rings 2 and 2 are firmly integrated without play and the workability of disassembly and assembly can be simplified. In addition, since the pair of inner rings 2 and 2 that are press-fitted and fixed to the axle can be removed integrally during repair or the like, there is no problem that only the inner-side inner ring 2 remains on the axle.

  Here, as shown in FIG. 1 (b), an annular large-diameter convex portion 4 b is formed at the large-diameter side end of the tapered roller 4, and the large end surface 4 a of the tapered roller 4 contacts the large flange 2 b of the inner ring 2. Rolling in contact. Since the length of the large-diameter convex portion 4b is smaller than the length of the grinding steal 2d of the inner ring 2, and is accommodated in the grinding steal 2d, the contact between the tapered roller 4 and the inner rolling surface 2a is obstructed. The durability of the bearing can be ensured. In the present embodiment, the contact point P between the large collar 2b of the inner ring 2 and the large end surface 4a of the tapered roller 4 is disposed on the extended line of the generatrix of the inner rolling surface 2a, and the tapered roller in the double row tapered roller bearing 1 is used. The contact distance e between 4 and the large bowl 2b is set to be substantially zero. As a result, the contact point P is applied to the edge to prevent the occurrence of seizure due to excessive surface pressure, and the rotational torque due to the slip between the large collar 2b and the large end surface 4a is theoretically zero, thereby reducing the rotational torque. A wheel bearing device can be provided.

  FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. In this embodiment, the outer ring rotation type of the above-described embodiment is basically changed to the inner ring rotation type, and the same reference numerals are used for the same parts or the same parts as the first embodiment. The detailed description is omitted.

  This wheel bearing device includes a double-row tapered roller bearing 10 and a hub ring 11 on which the double-row tapered roller bearing 10 is fitted. The hub wheel 11 is externally fitted to an outer joint member 12 constituting a constant velocity universal joint via a serration (or spline) 11c, and a wheel mounting flange 13 for mounting a wheel (not shown) to an end portion on the outer side. And a cylindrical small-diameter step portion 11b extending in the axial direction from the wheel mounting flange 13 via the shoulder portion 11a is formed. A plurality of hub bolts 13 a are implanted in the circumferentially equidistant position of the wheel mounting flange 13.

  The hub wheel 11 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and is induction-hardened from the shoulder portion 11a serving as the base of the wheel mounting flange 13 to the small diameter step portion 11b. The surface hardness is 50 to 64 HRC. Thereby, it has sufficient mechanical strength with respect to the rotational bending load applied to the wheel mounting flange 13, the wear resistance of the fitting surface with the inner ring 2 is improved, and the durability of the hub wheel 11 is improved. .

  The double row tapered roller bearing 10 includes a pair of inner rings 2, 2 and an outer ring (outer member) 14, and double row tapered rollers 4, 4 accommodated between the inner ring 2 and the outer ring 14. In a state where 2 is abutted against the shoulder 11a, the pair of inner rings 2 and 2 are press-fitted into the small-diameter step portion 11b through a predetermined shimoshiro.

  The outer ring 14 integrally has a vehicle body mounting flange 14a to be attached to the knuckle 15 on the outer periphery, and tapered double-row outer rolling surfaces 3a and 3a are formed on the inner periphery. This outer ring 14 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer raceway surfaces 3a and 3a have a surface hardness in the range of 58 to 64HRC by induction hardening. It has been cured.

  The outer joint member 12 is integrally formed with a shaft portion 17 that extends in the axial direction from a shoulder portion 16 that abuts on the inner ring 2 on the inner side. The shaft portion 17 has a serration (or spline) 17a that engages with the serration 11c of the hub wheel 11, and a male screw 17b formed at the end of the serration 17a. The hub wheel 11 and the outer joint member 12 are detachably fixed in the axial direction by a fixing nut 18 in a state where the double row tapered roller bearing 10 is sandwiched between the shoulder portion 16 and the hub wheel 11.

  Here, as in the above-described embodiment, the contact point P between the large collar 2b of the inner ring 2 and the large end face 4a of the tapered roller 4 is disposed on the extension of the generatrix of the inner rolling surface 2a, and the large collar 2b and the large end face Rotational torque due to sliding with 4a is reduced.

  FIG. 3 is a longitudinal sectional view showing a double-row tapered roller bearing in a third embodiment of the wheel bearing device according to the present invention. In this embodiment, the first embodiment described above (FIG. 1) is changed to a first generation structure, and the same reference numerals are used for the same parts or parts having the same functions as those of the first embodiment. The detailed description is omitted.

  This double-row tapered roller bearing 19 includes an outer ring 20 fitted to a knuckle (not shown), a pair of inner rings 2 and 2 press-fitted into a hub ring (not shown), and double-row tapered rollers 4 and 4. And. The outer ring (outer member) 20 is made of high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 58 to 64 HRC to the core portion by quenching. As in the above-described embodiment, the contact point P between the large collar 2b of the inner ring 2 and the large end face 4a of the tapered roller 4 is disposed on the extension of the generatrix of the inner rolling surface 2a, and the large collar 2b and the large end face 4a. Rotational torque due to slippage with is reduced.

  FIG. 4 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention. In this embodiment, the second embodiment described above (FIG. 2) is changed to a third generation structure, and the same parts or parts having the same functions as those in the above embodiment are denoted by the same reference numerals. Detailed description thereof will be omitted.

  The wheel bearing device includes an outer ring 14, a hub ring 21, and an inner member 22 including an inner ring 2 press-fitted into the hub ring 21. The hub wheel 21 integrally has a wheel mounting flange 13 at an end portion on the outer side, and has one (outer side) inner rolling surface 21a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 21a. A small diameter step portion 21b is formed, and a serration 11c is formed on the inner periphery. And the inner ring | wheel 2 in which the inner side rolling surface 2a of the other (inner side) was formed in the outer periphery is press-fitted through the predetermined diameter part 21b through predetermined | prescribed shimeshiro. A large collar 21c for guiding the tapered roller 4 is formed on the large diameter side of the inner raceway surface 21a of the hub wheel 21, and a small collar 21d for preventing the tapered roller 4 from falling off is formed on the small diameter side. .

  The hub wheel 21 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and extends from the seal land portion 13b serving as the base portion of the wheel mounting flange 13 to the inner rolling surface 21a and the small diameter step portion 21b. Then, the surface hardness is set to a range of 58 to 64 HRC by induction hardening. As a result, not only the wear of the seal land portion 13b with which the seal 23 is slidably contacted is suppressed, but it has sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 13 and is fitted to the inner ring 2. The wear resistance of the surface is improved, and the durability of the hub wheel 21 is improved.

  Here, as in the above-described embodiment, the contact point P between the large collars 21c, 2b of the hub wheel 21 and the inner ring 2 and the large end surface 4a of the tapered roller 4 is disposed on the extension line of the generatrix of the inner rolling surface 2a. Rotational torque due to slippage between the large collars 21c, 2b and the large end face 4a is reduced.

  Fig.5 (a) is a longitudinal cross-sectional view which shows 5th Embodiment of the bearing apparatus for wheels which concerns on this invention, (b) is a principal part enlarged view of (a). In this embodiment, the large hook of the first embodiment (FIG. 1) is basically provided on the outer ring side, and other parts are the same as the above-described embodiment or have the same function. Are given the same reference numerals and their detailed description is omitted.

  This double-row tapered roller bearing 1 ′ includes an outer ring 24 in which a hub flange 3 b for attaching a hub (not shown) is integrally formed at one end of the outer periphery, a pair of inner rings 25, 25, Double row tapered rollers 4 and 4 accommodated between the outer ring 24 and the outer ring 24 are provided.

  Tapered double row outer rolling surfaces 3a, 3a are formed on the inner periphery of the outer ring 24, and a large flange 24a for guiding the tapered roller 4 is formed on the larger diameter side of the outer rolling surfaces 3a, 3a. Has been. The outer ring 24 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the contact surface between the double row outer rolling surfaces 3a and 3a and the tapered surface of the large flange surface 24a is induction-hardened. Thus, the surface hardness is cured in the range of 58 to 64 HRC.

  On the other hand, the inner ring 25 has an inner rolling surface 2a facing the double row outer rolling surfaces 3a and 3a on the outer periphery, and a small flange 2c for preventing the tapered roller 4 from dropping off on the small diameter side of the inner rolling surface 2a. Is formed. In this embodiment, since the large collar 24a for guiding the tapered roller 4 is formed on the outer ring 24 side, no large collar is formed on the large diameter side of the inner raceway surface 2a of the inner ring 25. The large-diameter side is formed straight through an escape portion 25 a that allows the large-diameter convex portion 4 b of the tapered roller 4.

  Here, as shown in an enlarged view in FIG. 5 (b), an annular large-diameter convex portion 4 b is formed at the large-diameter side end of the tapered roller 4, and the large end surface 4 a of the tapered roller 4 is a large flange of the outer ring 24. Rolls in contact with 24a. The length of the large-diameter convex portion 4b is formed to be smaller than the length of the grinding steal 24b of the outer ring 24, and is accommodated in the grinding steal 24b. A contact point P between the large collar 24a of the outer ring 24 and the large end face 4a of the tapered roller 4 is disposed on the extended line of the generatrix of the outer rolling surface 3a, and the tapered roller 4 and the large collar in the double-row tapered roller bearing 1 ′. The contact distance e with 24a is set to be substantially zero. As a result, the contact point P is applied to the edge to prevent the occurrence of seizure due to the excessive surface pressure, and the rotational torque due to the sliding between the large flange 24a and the large end surface 4a is theoretically zero, and the rotational torque of the bearing is reduced. Can be reduced.

  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 wheel bearing device according to the present invention can be applied to a wheel bearing device in which a wheel is rotatably supported by a double row tapered roller bearing.

BRIEF DESCRIPTION OF THE DRAWINGS (a) is a longitudinal cross-sectional view which shows the double row tapered roller bearing in 1st Embodiment of the wheel bearing apparatus which concerns on this invention. (B) is the principal part enlarged view of (a). It is a longitudinal cross-sectional view which shows 2nd Embodiment of the wheel bearing apparatus which concerns on this invention. It is a longitudinal cross-sectional view which shows the double row tapered roller bearing in 3rd Embodiment of the wheel bearing apparatus which concerns on this invention. It is a longitudinal cross-sectional view which shows 4th Embodiment of the wheel bearing apparatus which concerns on this invention. (A) is a longitudinal cross-sectional view which shows the double row tapered roller bearing in 5th Embodiment of the wheel bearing apparatus which concerns on this invention. (B) is the principal part enlarged view of (a). (A) is a longitudinal cross-sectional view which shows the conventional bearing device for wheels. (B) is the principal part enlarged view of (a). (C) is the other principal part enlarged view of (a).

Explanation of symbols

1, 1 ', 10, 19 ... Double row tapered roller bearings 2, 25 ... Inner rings 2a, 21a ...・ ・ ・ ・ Inner rolling surface 2b, 21c, 24a ・ ・ ・ ・ ・ ・ ・ ・ Large 2c, 21d ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Small 2d, 24b ・ ・ ・ ・ ・ ・... Grinding stealing 3, 14, 20, 24 ... Outer ring 3a ... Outer rolling surface 3b ... ········· Hub flange 3c ················· Roller 4a ············· Large end surface 4b ··············· Large diameter convex portion 5 ··········· Retainer 6, 7, 23 ··············· Seal 8・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Annular groove 9 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Connecting ring 11 ・ ・ ・ ・ ・ ・ ・ ・・ Hub wheel 11a, 16 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Shoulder portion 11b, 21b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Small diameter step portion 11c, 17a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・· Serration 12 · · · · · · · Outer joint member 13 · · · · · · Wheel mounting flange 13a · · · ·················································································.・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Knuckle 17 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Shaft 17b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・Male screw 18 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Fixing nut 2 ... Inner member 25a ... Relief 51 ... ... Axle 52 ... Double row tapered roller bearing 53 ... Inner ring 53a ... .... Inner rolling surface 53b ...・ Outer ring 54a ... Outer rolling surface 55 ... Outward flange 56 ... Hub 57 ... Brake rotor 58 ... Bolt 59・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Nut 60 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel mounting bolt 61 ... Tapered roller 61a ... Large end face 61b ... ··· Chamfer 62, 63 ············ Seal e ············· Contact distance f (x) with tapered roller ······················································ Function P ···················· Contact point T between the large spear and the tapered end of the tapered roller

Claims (5)

A wheel bearing device for rotatably supporting a wheel by a double row tapered roller bearing,
The double-row tapered roller bearing is an outer member in which a tapered double-row outer rolling surface is formed on the inner periphery,
It comprises at least one inner ring fitted to a hub ring integrally having a wheel mounting flange at one end or an axle, and has a tapered double row inner rolling surface facing the outer side rolling surface of the double row on the outer periphery. Formed inner member,
In the wheel bearing device comprising a double row tapered roller accommodated so as to be freely rollable between both rolling surfaces via a cage,
A large ridge for guiding the tapered roller is formed on the large-diameter side of the rolling surface of the outer member or the inner member, and a contact point between the large ridge and the large end surface of the tapered roller is the surface of the rolling surface. A wheel bearing device, wherein the wheel bearing device is arranged on an extension of a bus bar.   An annular large-diameter convex portion is formed at the large-diameter side end of the tapered roller, and an annular steal is formed on the large-diameter side of the rolling surface, and the large-diameter convex portion is accommodated in the steal. The wheel bearing device according to claim 1.   The inner member integrally has a wheel mounting flange at one end, and one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and the small diameter step portion from the inner rolling surface. 2. A hub ring formed, and an inner ring press-fitted into a small-diameter step portion of the hub ring and having the other inner rolling surface facing the outer rolling surface of the double row formed on the outer periphery. Or the wheel bearing apparatus of 2.   The wheel bearing device according to claim 1 or 2, wherein the inward member includes a pair of inner rings.   The wheel bearing device according to claim 4, wherein annular grooves are formed in an inner periphery of a front side end portion which is a butting portion of the pair of inner rings, and a connecting ring having a substantially U-shaped cross section is attached to the annular grooves. .

Images