JP4823269B2 - Wheel bearing device - Google Patents

Description

  The present invention relates to a wheel bearing device in an automobile or the like.

An automobile wheel is rotatably supported by a suspension device via a wheel bearing device. Functions required for the wheel bearing device include high load capacity and high rigidity. In addition, automobile parts are strongly required to be reduced in weight in order to improve fuel efficiency, and the weight reduction is also required in wheel bearing devices.
The conventional general wheel bearing device can satisfy the load capacity, but the rigidity at the time of turning of the vehicle may not always be sufficient. Further, it is necessary to improve the bearing rigidity when the vehicle turns for stable running of the automobile.
A double row bearing is used for the wheel bearing device, and the vehicle weight when traveling straight is designed to act on the center of the double row bearing. However, when the vehicle turns, a moment load is generated so that the hub flange is tilted by a lateral force applied to the tire. Therefore, it is required to increase the rigidity in the vicinity of the outboard side row in the double row.

As for increasing the rigidity of the outboard side row, for example, as shown in FIG. 5, the PCD (pitch circle diameter) of the rolling elements 7 in the outboard side row Lo among the double row rolling element rows Lo and Li, The thing larger than PCD of the rolling element 8 of the inboard side row | line | column Li is proposed (for example, patent document 1). In the same patent document 1, as another embodiment, instead of changing the PCD, it is also proposed to increase the number of rolling elements 7 in the outboard side row Lo than the number of rolling elements 8 in the inboard side row Li. Has been.
JP 2003-232343 A

As shown in Patent Document 1 or the like, increasing the PCD of the outboard side row Lo or increasing the number of rolling elements provides an excellent effect on increasing the bearing rigidity of the outboard side portion. However, in all of the conventional wheel bearing devices, consideration for the shape of the hub wheel is insufficient, and the effect of improving the rigidity of the outboard side portion is not sufficient.
For example, in the example of FIG. 5, the position Q at which the inner ring 19 fitted to the hub ring 18 is abutted against the inner ring fitting surface of the hub ring 18 is more outboard than the center position of the ball spans of both rows Lo and Li. The outer diameter of the shaft portion 18a of the hub wheel 18 is designed to match the diameter of the small diameter portion of the inner ring 19 (the diameter of the position Q). Therefore, the outer diameter of the shaft portion 18a of the hub wheel 18 is abruptly reduced at a position slightly shifted from the raceway surface 5 on the outboard side to the inboard side, and the rigidity of the outboard side portion of the hub wheel 18 is not good. It is enough.

  An object of the present invention is to provide a wheel bearing device that can increase the rigidity of an outboard side portion while suppressing an increase in bearing weight.

The wheel bearing device according to the present invention includes an outer member having a double-row raceway surface on the inner periphery and a mounting portion for the vehicle body on the outer periphery, and an inner member having a double-row raceway surface facing each of the raceway surfaces on the outer periphery. The inner member has a hub flange for wheel attachment on the outboard side and a small diameter in a stepped shape on the inboard side. In a wheel bearing device comprising a hub ring having an inner ring fitting surface and an inner ring fitted to the inner ring fitting surface of the hub wheel, and forming the raceway surface of each row on the hub ring and the inner ring,
The bearing parts of both rows are back-to-back angular contact ball bearings, and the position where the inner ring is abutted against the end of the inner ring fitting surface of the hub ring is more than the center position between the rows of the rolling elements of the double row. On the inboard side, the shaft portion of the hub wheel is a straight shaft portion having a constant outer diameter at the center position between both rolling element rows, and a tapered diameter change in which the inboard side has a small diameter from the straight shaft portion. Following the stepped inner ring fitting surface through the portion, the portion on the outboard side with respect to the raceway surface of the inner ring has a smaller diameter portion that is smaller than the minimum diameter that is the groove bottom diameter of the raceway surface. and then, the outer diameter of the end face of the inner ring fitting surface of the hub wheel is approximately the same dimension as the outer diameter of the end portion of the smaller diameter portion of said inner ring, before Symbol inner ring, the inboard end of the hub Check that the extended cylindrical part is fixed to the hub ring by a crimped part that is crimped to the outer diameter side. And butterflies.

According to this configuration, since the outer diameter of the hub wheel at the center position between both rolling element rows is made larger than the minimum diameter of the raceway surface on the inboard side, the moment load at the time of vehicle traveling acting on the bearing device is reduced. The rigidity of the hub wheel can be increased. In all of the conventional bearing devices, the outer diameter of the hub ring between both rolling element rows is matched with the groove bottom diameter of the raceway surface of the inboard side row. Greatly contributes to improved rigidity. Increasing the diameter and thickness of each part in the bearing device leads to increased rigidity, but as a result of analysis, increasing the outer diameter of the hub ring between both rolling element rows is effective in improving rigidity against the moment load. I found out that Therefore, by increasing the outside diameter of this portion, cutting meat in other parts of the bearing device, without an increase in the weight, Ru can achieve improved rigidity.

In the present invention, the pitch circle diameter of the rolling element row on the outboard side may be larger than the pitch circle diameter of the rolling element row on the inboard side.
Increasing the pitch circle diameter of the outboard side row itself contributes to improving the bearing rigidity of the outboard side portion, but if the pitch circle diameter of the outboard side row is increased, the hub wheel between the rolling element rows is increased. The design to increase the outer diameter becomes easy. That is, even if the portion between both rolling element rows of the hub wheel is larger than the groove bottom diameter of the raceway surface of the inboard side row, it can be made smaller than the raceway groove bottom diameter of the outboard side. It does not impede the ability to incorporate rolling elements into the raceway surface of the hub wheel that is a row. Therefore, it is possible to increase the outer diameter of the portion between the two rolling element rows of the hub wheel without deteriorating the incorporation of the rolling elements.

As a configuration for shaving the bearing device, a meat stealing portion may be provided between the raceway surfaces of both rows on the inner diameter surface of the outer member.
According to the analysis, the portion between the raceway surfaces of both rows on the inner diameter surface of the outer member has little influence on the bearing rigidity, and even if the meat stealing portion formed of the circumferential groove is provided on the inner diameter surface, the rigidity is reduced. There is almost no influence. Therefore, by increasing the outer diameter of the central position between both rolling element rows of the hub wheel and providing a meat stealing part in the portion between the two rolling element rows of the outer member, it is possible to increase the weight without increasing the weight. The bearing rigidity can be increased.

As a configuration for shaving the bearing device, in addition to the above, a configuration for deepening the front recess for stealing the meat provided on the end surface of the hub wheel on the outboard side can be employed. The depth of the front recess may be deeper than the axial position of the center of the rolling element on the hub wheel side.
Even if the front concave portion is provided, the influence on the rigidity reduction of the hub wheel is small. If the intermediate outer diameter between both rolling element rows of the hub wheel is increased as in the present invention, the front concave portion can be made deeper, so that the bearing on the outboard side without increasing the weight. Stiffness can be increased.

In the present invention, the portion adjacent to the inboard side of the raceway surface formed on the hub wheel may be formed in the diameter changing portion so that the diameter gradually becomes smaller than the minimum diameter of the raceway surface.
In the case of this configuration, the diameter changing portion may be formed in a circular arc shape in cross section, and the radius of curvature thereof may be larger than the radius of curvature of the cross section of the raceway surface of the hub wheel. The diameter changing portion may be tapered.

When the portion adjacent to the inboard side of the raceway surface on the outer diameter surface of the hub ring is formed in a diameter changing portion that is smaller than the minimum diameter of this raceway surface, the hub wheel has a smaller outer diameter, thereby reducing the hub The wheel is lightened. In this case, if there is a sudden change in the outer diameter, the rigidity of the outboard side portion of the hub wheel will be reduced, but by gradually changing the diameter to a smaller diameter portion, the rigidity of the outboard side portion of the hub wheel will be increased. However, an increase in weight can be avoided.
When the diameter-changing portion is formed in a circular arc shape and the radius of curvature is larger than the radius of curvature of the cross-section of the raceway surface of the hub ring, the rigidity of the outboard side portion of the hub ring is further increased. Can be increased.

The wheel bearing device according to the present invention includes an outer member having a double-row raceway surface on the inner periphery and a mounting portion for the vehicle body on the outer periphery, and an inner member having a double-row raceway surface facing each of the raceway surfaces on the outer periphery. The inner member has a hub flange for wheel attachment on the outboard side and a small diameter in a stepped shape on the inboard side. In a wheel bearing device comprising a hub ring having an inner ring fitting surface and an inner ring fitted to the inner ring fitting surface of the hub wheel, and forming the raceway surface of each row on the hub ring and the inner ring, The bearing parts of both rows are back-to-back angular contact ball bearings, and the position where the inner ring is abutted against the end of the inner ring fitting surface of the hub ring is more than the center position between the rows of the rolling elements of the double row. On the inboard side, the shaft portion of the hub wheel is the shaft of the hub wheel. Is a straight shaft portion having a constant outer diameter at the center position between both rolling element rows, and the stepped portion-shaped inner ring fitting through a tapered diameter changing portion having a small diameter on the inboard side from the straight shaft portion. A portion on the outboard side of the raceway surface of the inner ring that is a diameter-reduced portion smaller than the minimum diameter that is the groove bottom diameter of the raceway surface, and the inner ring fitting surface of the hub ring. the outer diameter of the end face of substantially the same dimension as the outer diameter of the end portion of the smaller diameter portion of said inner ring, before Symbol inner ring, the cylindrical portion is extended to the inboard end of the hub to the outer diameter side It is characterized by being fixed to the hub wheel by a crimped caulking portion.

  A first embodiment of the present invention will be described with reference to FIGS. This embodiment is a third generation inner ring rotating type and is applied to a wheel bearing device for supporting a driven wheel. In this specification, the side closer to the outer side in the vehicle width direction of the vehicle when attached to the vehicle is referred to as the outboard side, and the side closer to the center of the vehicle is referred to as the inboard side.

  The wheel bearing device includes an outer member 1 having double-row raceway surfaces 3 and 4 formed on the inner periphery, and an inner member having raceway surfaces 5 and 6 facing the raceway surfaces 3 and 4 on the outer periphery. 2 and double-row rolling elements 7 and 8 interposed between the raceway surfaces 3 and 5 and the raceway surfaces 4 and 6 facing each other of the outer member 1 and the inner member 2. This wheel bearing device is a double-row angular ball bearing type, and the rolling elements 7 and 8 are formed of balls, and are held by cages 9 and 10 for each row. Each of the track surfaces 3 to 6 has a circular arc cross section, and the track surfaces 3 to 6 are formed so that the contact angle θ is aligned with the back surface. That is, the bearing portions 11 and 12 of each row Lo and Li are angular ball bearings and are back to back. The outboard side end in the bearing space between the outer member 1 and the inner member 2 is sealed with a seal 13, and the inboard side end is sealed with a cap (not shown) covering the entire bearing end surface. A magnetic encoder 14 for detecting the rotational speed is attached to the outer periphery of the inboard side end of the inner member 2.

The outer member 1 is a member on the fixed side, and as a mounting portion 16 to be attached to the knuckle 15 in a suspension device (not shown) of the vehicle body, a knuckle fitting portion 16a for fitting the knuckle 15 and a vehicle body fixing. A flange 16b is provided. The knuckle fitting portion 16a is provided at the inboard side end of the outer member 1, and the vehicle body fixing flange 16b is provided adjacent to the knuckle fitting portion 16a. The vehicle body fixing flange 16b is partially provided at a plurality of locations in the circumferential direction, and has a bolt insertion hole 17 formed of a screw hole, and a fixing bolt (not shown) inserted through the knuckle is inserted into the bolt insertion hole 17. The wheel bearing device is fixed to the knuckle 15 by screwing into the knuckle 15. A nut may be used instead of the screw insertion hole 17 as a screw hole.
The knuckle fitting portion 16a has a smaller diameter than other portions of the outer member 1, and the track surface 4 on the inboard side of the outer member 1 is located at an axial position where the knuckle fitting portion 16a is located. ing.

  The inner member 2 is a member on the rotation side, and is composed of a hub ring 18 and an inner ring 19, the raceway surface 5 on the outboard side on the hub wheel 18, and the raceway surface 6 on the inboard side on the inner ring 19. Are formed respectively. The hub wheel 18 has a hub flange 20 for attaching a wheel on the outer periphery of the shaft portion 18a on the outboard side, and an inner ring fitting surface 21 having a small diameter in a stepped portion on the outer periphery of the shaft portion 18a on the inboard side. is doing. The inner ring 19 is fitted to the inner ring fitting surface 21 of the hub ring 18 and is fixed to the hub ring 18 by a caulking portion 22 of the hub ring 18. The caulking portion 22 is formed by caulking a cylindrical portion extended to the inboard side end of the hub wheel 18 toward the outer diameter side by rolling caulking or the like.

  The hub flange 20 has bolt insertion holes 23 at a plurality of locations in the circumferential direction, and the bolts 24 are press-fitted into the bolt insertion holes 23. A brake disc and a wheel (both not shown) are stacked on the side surface of the hub flange 20 on the outboard side, and are fixed by nuts (not shown) screwed into the bolts 24. The hub flange 20 is continuous over the entire circumference, but the peripheral portions of the bolt insertion holes 23 at a plurality of locations in the circumferential direction are radially thickened portions 20a (FIG. 3), and the adjacent thickened portions 20a A hollow portion 25 for weight reduction is provided in the thin wall portion.

  A pilot portion 26 for guiding the inner surface of the brake disc and the wheel protrudes from the proximal end of the side surface on the outboard side of the hub flange 20. The pilot portion 26 is formed into a cylindrical shape by forming a front recess 27 for stealing meat provided on the front surface of the hub wheel 18.

  The dimensional relationship between the rows Lo and Li of the rolling elements 7 and 8 in both rows is such that the pitch circle diameter PCDo of the balls 7 of the rolling body row Lo on the outboard side is the pitch circle of the balls 8 of the rolling body row Li on the inboard side. The diameter is larger than PCDi. The ball diameters of the rolling elements 7 and 8 in both rows Lo and Li are the same, but due to the difference in the pitch circle diameters PCDo and PCDi, the number of balls 7 in the outboard side row Lo is determined as the number of balls in the inboard side row. It is possible to arrange more than eight. For example, the number of balls in the outboard side row Lo is 19 and the number of balls in the inboard side row Li is 17. The contact angles θ of both rows Lo and Li are the same, for example, 40 degrees.

The outer peripheral shape of the shaft portion 18a of the hub wheel 18 is such that the outer diameter D1 at the center position P between the rolling element rows Lo and Li is larger than the minimum diameter D2 that is the groove bottom diameter of the raceway surface 6 on the inboard side. ing. The center position P is a position that is the center of the rolling element spans W of both rows Lo and Li. The position Q where the inner ring 19 is abutted against the end of the inner ring fitting surface 21 of the hub ring 18 is on the inboard side with respect to the center position P.
As shown in FIG. 2 in an enlarged manner, the portion between the rolling element rows Lo and Li of the shaft portion 18a of the hub wheel 18 has the following shape dimensions in detail. The track surface 5 on the outboard side has a minimum diameter D3 at the center of the ball, and this minimum diameter D3 portion extends slightly toward the inboard side (about a fraction of the ball diameter) from the center of the ball. The outer diameter surface of the hub wheel shaft portion 18a has a portion adjacent to the inboard side of the raceway surface 5 as a first diameter changing portion 18aa having a circular arc shape having a small diameter toward the inboard side, and from this diameter changing portion 18aa Following the straight shaft portion 18ab having a constant outer diameter, it continues to the step-shaped inner ring fitting surface 21 via a tapered second diameter changing portion 18ac having a small diameter on the inboard side from the straight shaft portion 18ab. . The outer diameter of the straight shaft portion 18ab is the outer diameter D1 at the center position P.

The radius of curvature R1 in the arc-shaped curve of the cross section of the first diameter changing portion 18aa is larger than the radius of curvature of the cross section of the raceway surface 5, and is about twice as large, for example. As an example of dimensions, when the groove radius of curvature of the raceway surface 5 is 10 mm, the radius of curvature R1 of the diameter changing portion 18aa is about 20 mm.
The inner ring 19 has a portion 19 a that is on the outboard side of the raceway surface 6 and has a smaller diameter portion 19 a that is smaller than the minimum diameter D <b> 2 that is the groove bottom diameter of the raceway surface 6. The outer diameter of the end face, that is, the minimum diameter of the second diameter changing portion 18ac is substantially the same as the diameter of the end portion of the inner ring reduced diameter portion 19a.
In addition, the cross section of the diameter changing portion 18aa may be a taper shape, or may be any shape as long as the diameter gradually becomes smaller.

  The depth of the front concave portion 27 in the hub wheel 18 is deeper than the axial position A at the center of the rolling element 7 on the hub wheel 18 side. In this embodiment, the depth of the front concave portion 27 is set to a depth near the minimum diameter portion of the first diameter changing portion 18aa of the hub wheel shaft portion 18a, that is, to the vicinity of the end portion of the straight shaft portion 18ab. The cross-sectional shape of the front concave portion 27 is a shape that gradually becomes smaller in diameter toward the bottom, and the vicinity of the straight line M that forms the contact angle θ is a shape that forms a raised portion 27 a that rises to the inside of the front concave portion 27.

  A meat stealing portion 28 formed of a circumferential groove is provided between the raceway surfaces 3 and 4 of both rows Lo and Li on the inner diameter surface of the outer member. The meat stealing portion 28 has an axial width that is about half of the axial dimension between both the raceway surfaces 3 and 4, and its depth is substantially the same as the groove bottom of the raceway surface 3 on the outboard side. .

  According to this configuration, the outer diameter D1 of the hub wheel 18 at the central position P between the rolling element rows Lo and Li is made larger than the minimum diameter D2 of the raceway surface 6 of the inboard side row Li, and thus acts on the bearing device. The rigidity of the hub wheel 18 can be increased with respect to the moment load during traveling of the vehicle. In all of the conventional bearing devices, the outer diameter of the hub wheel between both rolling element rows is matched to the groove bottom diameter of the raceway surface of the inboard side row. , Greatly contribute to the improvement of rigidity. Increasing the diameter and thickness of each part in the bearing device leads to increased rigidity, but as a result of FEM analysis (analysis by electrolytic electron microscope), the outer diameter of the hub ring 18 between the rolling element rows Lo and Li is increased. It has been found that it is efficient to improve the rigidity against the moment load. Therefore, by increasing the outer diameter D1 of this portion, it is possible to cut the flesh of other portions of the bearing device and achieve an improvement in rigidity without accompanying an increase in weight.

As a configuration for cutting the meat of the bearing device, a meat stealing portion 28 formed of a circumferential groove is provided between the raceway surfaces 3 and 4 of both rows Lo and Li on the inner diameter surface of the outer member 1.
According to the analysis, the portion between the raceway surfaces 3 and 4 of both rows Lo and Li on the inner diameter surface of the outer member 1 has little influence on the bearing rigidity. Even if the meat stealing portion 28 is provided on the inner diameter surface, the rigidity is increased. There is almost no impact on the decline. Therefore, by increasing the intermediate outer diameter D1 between the rolling element rows Lo and Li of the hub wheel 1 and providing the meat stealing portion 28 on the outer member 1, the weight on the outboard side can be increased without increasing the weight. The bearing rigidity can be increased.

  In this embodiment, since the pitch circle diameter PCDo of the balls 7 in the outboard side row Lo is increased, the bearing rigidity of the outboard side portion is improved. As for the number of rolling elements 7 and 8, since the number of outboard side rows Lo is increased, the bearing rigidity of the outboard side portion is further improved. As the pitch circle diameter PCDo of the outboard side row Lo becomes larger, the hub wheel outer diameter D1 at the center position P between the rolling element rows Lo and Li can be easily designed as described above. That is, even if the portion between the rolling element rows Lo and Li of the hub wheel 18 is larger than the groove bottom diameter D2 of the raceway surface 6 of the inboard side row Li, the raceway groove bottom diameter of the outboard side row Lo. Since it can be made smaller than D3, the incorporation of the rolling elements 7 into the bubbling raceway surface 5, which is the outboard side row Lo, is not hindered.

  Regarding the outer diameter surface shape of the bearing portion 18 a of the hub wheel 18, a portion adjacent to the inboard side of the raceway surface 5 of the hub wheel 18 is a diameter changing portion 18 aa having a smaller diameter than the minimum diameter D3 of the raceway surface 5. Therefore, the hub wheel 18 is reduced in weight by reducing the outer diameter of the hub wheel 18. In this case, if there is a sudden change in the outer diameter, the rigidity of the outboard side portion of the hub wheel 18 is lowered. Since the radius of curvature is larger than 5, the weight increase can be avoided while increasing the rigidity of the portion of the hub wheel 18 on the outboard side.

  Further, since the front concave portion 27 provided on the end surface on the outboard side of the hub wheel 18 is deeper than the axial position A at the center of the rolling element 7 on the hub wheel 18 side, the amount of stealing meat by the front concave portion 27 can be increased. Thus, the weight can be further reduced. Even if the front concave portion 27 is provided, the influence on the rigidity reduction of the hub wheel 18 is small, and when the intermediate outer diameter D1 between the rolling element rows Lo and Li of the hub wheel 18 is increased as in this embodiment, Even if the front recess 27 is deepened as described above, rigidity can be ensured. This also increases the bearing rigidity on the outboard side while suppressing an increase in weight. In this example, the shape of the front concave portion 27 is such that the vicinity of the straight line M forming the contact angle θ is a raised portion 27a that rises inward of the front concave portion 27. Therefore, the inner diameter of the front concave portion 27 is made as large as possible. Therefore, the required rigidity can be secured while further reducing the weight.

FIG. 4 shows a reference proposal example . This proposed example is a third generation inner ring rotating type and is applied to a wheel bearing device for supporting a driving wheel. In the wheel bearing device according to the first embodiment described with reference to FIGS. 1 to 3, a drive shaft coupling hole 31 is provided through the central portion of the hub wheel 18 in the inner member 2. The drive shaft coupling hole 31 is a hole that penetrates the stem portion of the outer ring serving as one joint member of a constant velocity joint (not shown), and a spline groove 31a that meshes with the spline of the stem portion is formed on the inner diameter surface. ing. The front concave portion 27A is provided as a counterbore portion in which a nut (not shown) to be screwed into the male screw portion at the tip of the stem portion is accommodated. The inner ring 19 is fixed to the hub ring 18 by pressing a part of the constant velocity joint outer ring against the width surface of the inner ring 19 by tightening the nut. Further, the inboard side end in the bearing space between the outer member 1 and the inner member 2 is sealed with a seal 32, and the magnetic encoder 14 also serves as a slinger in the seal 32. Other configurations in the proposed example are the same as those in the first embodiment.
When applied to a wheel bearing device for driving wheel support in this way, each effect such as increasing the rigidity of the outboard side portion while suppressing an increase in bearing weight can be obtained as in the above embodiment. It is done.

It is sectional drawing of the wheel bearing apparatus concerning one Embodiment of this invention. It is a partial expanded sectional view of the same bearing device. It is the side view which looked at the same bearing device for wheels from the inboard side. It is sectional drawing of the wheel bearing apparatus concerning a reference proposal example . It is sectional drawing of a prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Outer member 2 ... Inner member 3-6 ... Raceway surface 7, 8 ... Rolling element 11, 12 ... Bearing part 15 ... Knuckle 16 ... Mounting part 18 ... Hub wheel 18a ... Shaft part 18aa of hub wheel ... Diameter change Part 18ab ... Straight shaft part 19 ... Inner ring 20 ... Hub flange 27 ... Front concave part 28 ... Meat stealing part PCDi ... Pitch circle diameter PCDo on the inboard side Pitch circle diameter D1 on the outboard side ... Outer diameter D2 on the intermediate part ... Inn Minimum diameter of raceway surface on board side

Claims (7)

An outer member having a double-row raceway surface on the inner periphery and a mounting portion for the vehicle body on the outer periphery, an inner member having a double-row raceway surface on the outer periphery facing each of the raceway surfaces, and the facing raceway surface An inner ring in which the inner member has a hub flange for mounting a wheel on the outboard side of the shaft portion and has a small diameter in a stepped portion on the inboard side of the shaft portion. In the wheel bearing device comprising a hub ring having a fitting surface and an inner ring fitted to the inner ring fitting surface of the hub ring, and forming the raceway surface of each row on the hub ring and the inner ring,
The bearing parts of both rows are back-to-back angular contact ball bearings, and the position where the inner ring is abutted against the end of the inner ring fitting surface of the hub ring is more than the center position between the rows of the rolling elements of the double row. On the inboard side, the shaft portion of the hub wheel is a straight shaft portion having a constant outer diameter at the center position between both rolling element rows, and a tapered diameter change in which the inboard side has a small diameter from the straight shaft portion. Following the stepped inner ring fitting surface through the portion, the portion on the outboard side with respect to the raceway surface of the inner ring has a smaller diameter portion that is smaller than the minimum diameter that is the groove bottom diameter of the raceway surface. and then, the outer diameter of the end face of the inner ring fitting surface of the hub wheel is approximately the same dimension as the outer diameter of the end portion of the smaller diameter portion of said inner ring, before Symbol inner ring, the inboard end of the hub Check that the extended cylindrical part is fixed to the hub ring by a crimped part that is crimped to the outer diameter side. Wheel bearing device and butterflies.   2. The wheel bearing device according to claim 1, wherein the pitch circle diameter of the rolling body row on the outboard side is larger than the pitch circle diameter of the rolling body row on the inboard side.   The wheel bearing device according to claim 1 or 2, wherein a meat stealing portion is provided between the raceway surfaces of both rows on the inner diameter surface of the outer member.   The hub ring according to any one of claims 1 to 3, wherein the hub wheel has a front recess for stealing meat on an end surface on an outboard side, and a depth of the front recess is determined by the rolling element on the hub wheel side. Wheel bearing device that is deeper than the central axial position.   5. The diameter change portion according to claim 1, wherein a portion adjacent to the inboard side of the raceway surface formed on the hub wheel has a diameter that gradually becomes smaller than a minimum diameter of the raceway surface. A bearing device for a wheel which is formed.   In Claim 5, the diameter change part adjacent to the inboard side of the raceway surface formed in the said hub ring is formed in cross-sectional arc shape, and the curvature radius is larger than the curvature radius of the cross section of the raceway surface of the said hub ring. Wheel bearing device.   6. The wheel bearing device according to claim 5, wherein a diameter-changing portion adjacent to the inboard side of the raceway surface formed on the hub wheel has a tapered shape.

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