JP5425610B2 - Wheel bearing device - Google Patents

Description

  The present invention relates to a wheel bearing device for rotatably supporting a wheel with respect to a vehicle body in a vehicle such as an automobile.

  The wheel bearing device has evolved from a structure called the first generation, which uses a combination of double row rolling bearings, to a second generation in which the body mounting flange is integrally provided on the outer member. One of the two inner raceways of the rolling bearing is formed on the outer circumference of the hub ring, and one of the two inner raceways of the double row rolling bearing is formed on the outer circumference of the hub ring. At the same time, a fourth-generation one having the other formed on the outer periphery of the outer joint member of the constant velocity universal joint has been developed.

  For example, Patent Document 1 describes what is called a third generation. As shown in FIG. 43, a wheel bearing device called a third generation includes a hub wheel 152 having a flange 151 extending in the outer diameter direction, and a constant velocity universal joint 154 to which an outer joint member 153 is fixed. And an outer member 155 disposed on the outer peripheral side of the hub wheel 152.

  The constant velocity universal joint 154 is disposed between the outer joint member 153, the inner joint member 158 disposed in the mouth portion 157 of the outer joint member 153, and the inner joint member 158 and the outer joint member 153. And a cage 160 for holding the ball 159. A female spline 161 is formed on the inner peripheral surface of the center hole of the inner joint member 158, and a male spline formed at the end of the shaft (not shown) is inserted into the center hole. By fitting the female spline 161 on the inner joint member 158 side and the male spline on the shaft side, the inner joint member 158 and the shaft are coupled so that torque can be transmitted.

  The hub wheel 152 includes a cylindrical portion 163 and a flange 151, and a short cylindrical pilot portion for mounting a wheel and a brake rotor (not shown) on the outer end surface 164 (end surface on the outboard side) of the flange 151. 165 protrudes. The pilot portion 165 includes a large diameter portion 165a and a small diameter portion 165b, and a brake rotor is externally fitted to the large diameter portion 165a, and a wheel is externally fitted to the small diameter portion 165b.

  A fitting portion 166 is provided on the outer peripheral surface of the end portion on the inboard side of the cylindrical portion 163, and the inner ring 167 is fitted to the fitting portion 166. A first inner raceway surface 168 is provided in the vicinity of the flange 151 on the outer peripheral surface of the cylindrical portion 163, and a second inner raceway surface 169 is provided on the outer peripheral surface of the inner ring 167. The flange 151 of the hub wheel 152 is provided with a bolt mounting hole 162, and a hub bolt for fixing the wheel and the brake rotor to the flange 151 is mounted in the bolt mounting hole 162.

  The outer member 155 of the rolling bearing is provided with two rows of outer raceways 170 and 171 on the inner periphery thereof, and a flange (vehicle body mounting flange) 182 on the outer periphery thereof. The first outer raceway surface 170 of the outer member 155 and the first inner raceway surface 168 of the hub wheel 152 face each other, and the second outer raceway surface 171 of the outer member 155 and the raceway surface 169 of the inner ring 167 face each other. The rolling elements 172 are interposed between these.

  The shaft portion 173 of the outer joint member 153 is inserted into the tube portion 163 of the hub wheel 152. A screw portion 174 is formed at the shaft end of the shaft portion 173, and a male spline 175 is formed at the outer diameter portion on the inboard side of the screw portion 174. In addition, a female spline 176 is formed on the inner diameter surface of the cylindrical portion 163 of the hub wheel 152, and the shaft portion 173 is press-fitted into the cylindrical portion 163 of the hub wheel 152, so that the male spline 175 on the shaft portion 173 side and the hub wheel 152 side. The female spline 176 is fitted.

  Then, the nut member 177 is screwed to the screw portion 174 of the shaft portion 173, and the hub wheel 152 and the outer joint member 153 are fixed. At this time, the seat surface 178 of the nut member 177 and the outer end surface 179 of the cylindrical portion 163 come into contact with each other, and the end surface 180 on the outboard side of the mouse portion 157 and the end surface 181 of the inner ring 167 come into contact with each other. As a result, the hub wheel 152 is sandwiched between the nut member 177 and the mouth portion 157 via the inner ring 167.

  However, when such a configuration is adopted, the outer joint member 153 and the hub ring 152 press the male spline 175 provided on the shaft portion 173 into the female spline 176 provided on the hub ring 152. Since they are coupled, it is necessary to perform spline processing on both the shaft portion 173 and the hub wheel 152, which increases costs. In addition, it is necessary to match the unevenness of the male spline 175 of the shaft portion 173 and the female spline 176 of the hub wheel 152 at the time of press-fitting. If it is press-fitted with a large diameter, the play in the circumferential direction is likely to occur. If there is a backlash in the circumferential direction, the torque transmission is inferior and abnormal noise may occur. Thus, when connecting the outer joint member 153 and the hub wheel 152, there is a problem of tooth surface damage during press-fitting and backlash during use, and it is difficult to avoid both at the same time. .

  Therefore, the applicant of the present application has proposed a wheel bearing device disclosed in Patent Document 2 in order to cope with such a problem. Specifically, a convex portion extending in the axial direction provided in one of the shaft portion of the outer joint member and the hole of the hub wheel is press-fitted into the other, and the concave portion is formed by the convex portion on the other side. Thus, a concave-convex fitting structure in which the entire fitting part between the convex part and the concave part is in close contact is configured. When the concave / convex fitting structure is configured, it is not necessary to previously form the spline portion on the member in which the concave portion is formed, so that productivity can be improved. Moreover, since the damage of the tooth surface at the time of press fit can be avoided, the stable fitting state can be maintained. Further, in the above-described concave / convex fitting structure, no gap is formed in which the play occurs in the radial direction and the circumferential direction, so that stable torque transmission is possible and the generation of abnormal noise is prevented. In addition, since the shaft portion is in close contact with the hole portion and the strength of the torque transmitting portion is improved, the length of the fitting portion can be shortened to make the bearing device compact in the axial direction.

  In addition, since said uneven | corrugated fitting structure can be isolate | separated by providing the pulling-out force of an axial direction in the state which removed the bolt member from the bolt hole provided in the axial part, favorable repair workability (maintenance) Gender) is secured. In addition, after the repair, the concave-convex fitting structure can be reconfigured by press-fitting the shaft portion of the outer joint member into the hole portion of the hub wheel. Reconstruction of the concave-convex fitting structure (recombination of the hub wheel and the outer joint member) can be performed by screwing the bolt member into the bolt hole provided in the shaft portion. Therefore, it is not necessary to use a large-scale facility such as a press-fitting press machine when reconstructing the concave-convex fitting structure. Accordingly, it is possible to easily inspect and repair the wheel bearing device even at a site such as an automobile maintenance factory.

JP 2004340403 A JP 2009-56869 A

  By the way, when the above-described concave / convex fitting structure is configured, the convex portion can be formed by various processing methods such as cutting, rolling, pressing, broaching, etc. In many cases, molding is performed by plastic working such as rolling or pressing.

  However, for example, when a convex portion is formed on the shaft portion of the outer joint member by using plastic processing, plastic processing becomes insufficient at the end of the convex portion on the press-fitting start side, and the shape of the processed convex portion is reduced. Is likely to occur. When sagging occurs in this way, the height direction dimension and circumferential thickness (tooth thickness) at the press-fitting start side end of the convex part are normal except for the press-fitting start side end part of the convex part due to processing failure due to sagging. It becomes relatively smaller than the part where plastic working has been performed. Therefore, when the shaft portion of the outer joint member is press-fitted into the hole of the hub wheel, it is more than the first cut at the end face on the press-fitting start side of the convex portion due to the part that has been normally plastic processed in the convex portion. There may be a problem that the hub wheel is pushed to the outer diameter side to expand.

  Therefore, in order to deal with such a problem, it is conceivable to preliminarily thicken the press-fitting start side where the sagging easily occurs in the shaft portion of the outer joint member before plastic working. New problems arise. That is, in this case, the height dimension and the circumferential thickness of the convex portion tend to be too large at the end of the press-fitting start side, and when the convex portion is press-fitted in this state, the press-fitting start of the convex portion is started. There is a possibility that a situation may occur in which the convex portion and the hole portion of the hub wheel are not closely fitted to each other at the end portion on the side, and sufficient strength cannot be obtained.

  Therefore, in order to maximize the advantages of the above-described uneven fitting structure without causing expansion of the hub wheel, it is extremely important to properly manage the shape of the convex portions constituting the uneven fitting structure. However, Patent Document 2 does not mention this point, and there remains a problem to be improved.

  In the above, the case where the convex portion is formed in the shaft portion of the outer joint member has been described as an example, but the problem such as the expansion of the hub ring is similarly caused when the convex portion is formed in the hole portion of the hub ring. Can occur. Also, not only when the convex part is formed by plastic deformation, but even when the convex part is formed by cutting or broaching, the same problem occurs if the shape of the convex part is inappropriate Needless to say.

  In view of the above circumstances, the present invention appropriately improves the shape of the convex portions constituting the concave-convex fitting structure, thereby improving the adhesion of the concave-convex fitting structure while preventing unreasonable expansion of the hub wheel. Making it a technical issue.

  The present invention, which has been devised to solve the above problems, includes an outer member having a double-row raceway surface on the inner periphery, and a hub wheel attached to the wheel, and the double-row facing the raceway surface of the outer member. Constant velocity universal joint having an inner member having a raceway surface on the outer periphery, a wheel bearing having a double row rolling element interposed between the outer member and the raceway surface of the inner member, and an outer joint member A convex portion extending in the axial direction provided in one of the shaft portion of the outer joint member and the hole portion of the hub wheel is press-fitted into the other, and the concave portion is formed by the convex portion in the other In the wheel bearing device in which the concave and convex fitting structure in which the entire fitting portion of the convex portion and the concave portion is in close contact with each other and the shaft portion of the outer joint member and the hub wheel are combined with each other, For each of the convex portions, the first dimension management target is the press-fitting start side end of the convex portion. The diameter D1 of the circle passing through the top of the convex portion with the axis centered at the axis perpendicular to the axis and the axis perpendicular to the axial center at any position X in the axial direction excluding the press-fitting start side end The diameter D2 (X) of the circle passing through the top of the portion is set, and the second dimension control target is the height direction of the convex portion with the axis centered at the axially perpendicular section at the press-fitting start side end portion. The circumferential thickness L1 of the projection on the reference circle passing through the intermediate portion of the projection, and the circumferential thickness L2 of the projection on the circle obtained by projecting the reference circle on the cross section perpendicular to the axis at the position X (X And a tolerance value of 0.2 mm or less is given to the value of | D1-D2 (X) | based on the object of the first dimension management, and the second dimension management. A tolerance of 0.1 mm or less is given to the value of | L1-L2 (X) | It is characterized in that the.

  In addition, although the uneven | corrugated fitting structure here is as above-mentioned, the fitting part whole region of a convex part and a recessed part closely_contact | adheres, A clearance gap may exist in a very small area | region of a fitting part. Since such a gap is inevitably generated in the formation process of the concave portion by the convex portion, even if there is such a gap, the concept that “the entire fitting part of the convex portion and the concave portion is in close contact” is used. It shall be included (hereinafter the same).

  According to the above configuration, the first dimension management target and the second dimension management target are the parameters (D1, L1) resulting from the shape of the convex portion at the press-fitting start side end portion that is likely to change in shape due to processing failure. ) Is set as one management item, and the parameters (D2 (X), L2 (X)) resulting from the shape of the projection at the position excluding the press-fitting start side end are set as another management item. The And if it sees about the object of the 1st dimensional control, the top part of a convex part will follow an axial direction, so that the absolute value (| D1-D2 (X) |) of the difference of D1 and D2 (X) becomes small. It becomes a straight line extending in parallel. Further, in terms of the second dimension management target, the smaller the absolute value (| L1−L2 (X) |) of the difference between L1 and L2 (X), the smaller the circumferential thickness of the convex portion. The tendency to become constant in the axial direction becomes stronger. Therefore, if these two dimensional control objects are managed within a predetermined range, the shape change of the convex portion in the axial direction becomes small in the axial direction, and the convex portion is press-fitted into the mating member to form an uneven fitting structure. In this case, it is possible to improve the adhesion of the concave-convex fitting structure while preventing the hub wheel from being unduly expanded. On the other hand, however, if the above two dimensional control targets are strictly controlled, special considerations are required for the processing of the convex portion, and the member (outer joint member or hub ring) on the side forming the convex portion is manufactured. Costs may increase unjustly. Therefore, in the present invention, in addition to setting the first dimension management target and the second dimension management target as management items, | D1-D2 (X) based on the first dimension management target An allowable value of 0.2 mm or less is given to the value of |, and 0.1 mm or less is given to the value of | L1-L2 (X) | based on the second dimension management target. It was decided to give an allowable value. As a result, it is possible to achieve a reduction in the manufacturing cost of the member on the side where the convex portion is formed while simultaneously preventing the unfavorable expansion of the hub wheel and improving the adhesion of the concave-convex fitting structure. .

  In the above configuration, the end surface on the press-fitting start side of the convex portion may be finished by cutting, and the edge of the end surface on the press-fitting start side may be provided with a corner portion that is not round and can be cut into the other end. In this way, by cutting into the other member with a rounded corner, the concave portion can be accurately formed in the other member, and an increase in press-fit load can be prevented.

  In the above configuration, a gap may be formed between a tooth bottom portion between the convex portions adjacent in the circumferential direction and a protruding portion formed on the other side and facing the tooth bottom portion in the radial direction. In this way, since the cut amount of the convex portion is reduced at the time of press-fitting, the moldability of the concave portion is improved and the frictional force is reduced by the amount of the gap, thereby reducing the pressure input at the time of press-fitting. Can do. Moreover, even if the press fitting is performed with the shaft center of the outer joint member and the shaft center of the hub wheel slightly deviated from each other, both can be assembled with the gap absorbed, so that the assembly work Time work management becomes easy.

  In the above configuration, when the convex portion is provided on the shaft portion of the outer joint member, the hardness of at least the end portion on the press-fitting start side of the convex portion is made higher than the inner diameter portion of the hole portion of the hub wheel. Preferably, when the convex portion is provided on the inner diameter surface of the hole portion of the hub wheel, the hardness of at least the end portion on the press-fitting start side of the convex portion is set to be larger than the outer diameter portion of the shaft portion of the outer joint member. It is preferable to increase the height. If it does in this way, the rigidity of the member by which the convex part is formed can be improved, and the biting property to the member of the other party of a convex part can be improved. Furthermore, in the latter case, since it is not necessary to perform the thermosetting treatment on the shaft side, the productivity of the outer joint member is excellent.

  In the configuration described above, a pocket portion may be provided in the shaft portion of the outer joint member or the hole portion of the hub wheel for accommodating the protruding portion generated by the formation of the concave portion by the press-fitting. In this way, since the protruding portion can be held in the pocket portion, the protruding portion does not enter the vehicle outside the apparatus. Therefore, since it is not necessary to perform the removal process of the protruding portion, the removal process can be omitted to reduce the number of assembling work, and the assembling workability can be improved and the cost can be reduced. Here, the “extrusion portion” is the amount of material corresponding to the volume of the concave portion formed by the convex portion, and is extruded from the concave portion to be formed, or cut to form the concave portion. It shall be comprised from what was extruded, what was extruded, and what was cut.

  Said structure WHEREIN: The said convex part is provided in several places of the circumferential direction, and the circumferential direction thickness of the said convex part is set between the said convex parts adjacent to the circumferential direction in the intermediate part of the height direction of the said convex part. It is preferable to make it smaller than the groove width. In this way, since the mating meat that has entered the groove between the adjacent convex portions has a large thickness in the circumferential direction, the shear area of the meat can be increased, and the torsional strength can be improved. Can do. Moreover, since the circumferential thickness of the convex portion is small, the press-fitting load can be reduced, and the press-fitting property can be improved. Such an effect is to make the sum of the circumferential thicknesses of the respective convex portions smaller than the sum of the groove widths between the convex portions adjacent in the circumferential direction at the intermediate portion in the height direction of the convex portions. But it is achieved as well.

  In the above-described configuration, a retaining structure for restricting retaining of the shaft portion may be provided between the shaft portion of the outer joint member and the inner diameter surface of the hub wheel. In this way, the situation in which the outer joint member comes off in the axial direction with respect to the hub wheel can be prevented by the retaining structure, so that a stable connection state between the two is maintained.

  In the above-described configuration, separation may be allowed by applying an axial pull-out force to the uneven fitting structure, and the hub wheel and the shaft portion of the outer joint member may be bolted via a bolt member. . By doing so, the outer joint member can be removed from the hole of the hub wheel by releasing the bolt fixing and applying an axial pulling force to the shaft portion of the outer joint member.・ Inspection workability (maintenance) can be improved. Further, by fixing with bolts, the axial disconnection of the outer joint member from the hub wheel is restricted, and stable torque transmission is possible over a long period of time.

  In the above configuration, the inner member includes the hub wheel and an inner ring that is press-fitted into the outer periphery of the end portion on the inboard side of the hub wheel, and the inner member is disposed on the outer periphery of the hub wheel and the outer periphery of the inner ring, respectively. A raceway surface may be formed. In this way, the raceway surfaces can be formed on the outer periphery of the hub wheel and the outer periphery of the inner ring, respectively. As a result, the wheel bearing device can be reduced in weight and size.

  According to the present invention, the shape of the convex portion constituting the concave-convex fitting structure can be appropriately managed based on the first dimension management target and the second dimension management target. It is possible to improve the adhesion of the concave-convex fitting structure while preventing unfair expansion. Therefore, the concave / convex fitting structure can stably maintain the coupling state between the hub wheel and the outer joint member, which can contribute to the improvement of the durability of the wheel bearing device.

It is sectional drawing which shows embodiment of the wheel bearing apparatus. (A) is sectional drawing of the uneven | corrugated fitting structure of the said wheel bearing apparatus, (b) is the X section enlarged view. It is explanatory drawing of the undesirable form regarding the convex part of an uneven | corrugated fitting structure. It is explanatory drawing of the desirable form regarding the convex part of an uneven | corrugated fitting structure. (A) And (b) is a perspective view which shows an example of the convex part of an uneven | corrugated fitting structure. The relationship between the diameter D1 of the circle passing through the top of the convex portion at the press-fitting start side end and the diameter D2 (X) of the circle passing through the top of the convex portion at a position away from the press-fitting start end to the axial distance X It is sectional drawing shown. (A) is sectional drawing which shows circumferential direction thickness L1 of one convex part in the press injection start side edge part, (b) is the same convex part in the position away from the press injection start side edge part to the axial distance X It is sectional drawing which shows circumferential direction thickness L2 (X). It is a figure of the bearing, hub wheel, and joint outer ring before the assembly of the wheel bearing device. It is sectional drawing which shows the assembly method of the said bearing apparatus for wheels. It is sectional drawing which shows the assembly method of the said bearing apparatus for wheels. (A) is an expanded sectional view when an O-ring is used as a sealing member, and (b) is an enlarged sectional view when a gasket is used. It is a perspective view which shows the other examples of the convex part of an uneven | corrugated fitting structure. (A)-(c) is each projection figure of Fig.12 (a)-(c). It is a perspective view which shows the other examples of the convex part of an uneven | corrugated fitting structure. (A) And (b) is a projection figure which shows the other example of the convex part of an uneven | corrugated fitting structure. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is sectional drawing which shows the assembly method of the wheel bearing apparatus of FIG. It is sectional drawing which shows the assembly method of the wheel bearing apparatus of FIG. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is sectional drawing which shows the assembly method of the wheel bearing apparatus of FIG. It is sectional drawing which shows the assembly method of the wheel bearing apparatus of FIG. It is a front view which shows the end surface of the axial part of the joint outer ring | wheel in the wheel bearing apparatus of FIG. 19, Comprising: (a) is the outer collar-shaped latching | locking part formed over the perimeter, (b) is along the circumferential direction. It is a figure which shows the outer collar-shaped latching | locking part arrange | positioned by the predetermined pitch, respectively. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is a principal part expanded sectional view of the wheel bearing apparatus of FIG. It is sectional drawing of the coupling outer ring | wheel before the assembly of the wheel bearing apparatus of FIG. It is explanatory drawing which shows the other desirable form regarding the convex part of the uneven | corrugated fitting structure shown in FIG. It is explanatory drawing which shows the other undesirable form regarding the convex part of an uneven | corrugated fitting structure. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is a principal part expanded sectional view of the wheel bearing apparatus of FIG. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is sectional drawing which shows before the assembly of the wheel bearing apparatus of FIG. It is a principal part expanded sectional view of the wheel bearing apparatus of FIG. It is sectional drawing which shows the isolation | separation process of the uneven | corrugated fitting structure in the wheel bearing apparatus of FIG. It is sectional drawing which shows the re-pressing process in the wheel bearing apparatus of FIG. (A) And (b) is sectional drawing which shows the other example of the convex part of an uneven | corrugated fitting structure. It is sectional drawing of the bearing before the assembly of the other example of the bearing apparatus for wheels, a hub ring, and a coupling outer ring. It is a principal part expanded sectional view of the wheel bearing apparatus of FIG. (A) is sectional drawing which shows the other example of an uneven | corrugated fitting structure, (b) is the Y section enlarged view. It is sectional drawing which shows other embodiment of the wheel bearing apparatus. It is sectional drawing of the conventional wheel bearing apparatus.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 shows a wheel bearing device according to a first embodiment. In this wheel bearing device, a double row wheel bearing 2 including a hub wheel 1 and a constant velocity universal joint 3 are integrated. In the following description, the inboard side means the side that is the inner side in the vehicle width direction when attached to the vehicle, and the outboard side means the outer side in the vehicle width direction of the vehicle when attached to the vehicle. Means the side.

  The constant velocity universal joint 3 is interposed between a joint outer ring 5 as an outer joint member, a joint inner ring 6 as an inner joint member disposed inside the joint outer ring 5, and a joint outer ring 5 and a joint inner ring 6. A plurality of balls 7 that transmit torque and a cage 8 that is interposed between the joint outer ring 5 and the joint inner ring 6 and holds the balls 7 are configured as main members. The joint inner ring 6 is spline-fitted by press-fitting the end portion 10a of the shaft 10 into the hole inner diameter 6a and is coupled to the shaft 10 so as to be able to transmit torque. Note that a retaining ring 9 for retaining the shaft is fitted to the end portion 10a of the shaft 10.

  The joint outer ring 5 includes a mouth portion 11 and a shaft portion (also referred to as a stem portion) 12. The mouth portion 11 has a bowl shape opened at one end, and a plurality of track grooves 14 extending in the axial direction on the inner spherical surface 13 thereof. Are formed at equal intervals in the circumferential direction. The track groove 14 extends to the open end of the mouse portion 11. In the joint inner ring 6, a plurality of track grooves 16 extending in the axial direction are formed on the outer spherical surface 15 at equal intervals in the circumferential direction.

  The track groove 14 of the joint outer ring 5 and the track groove 16 of the joint inner ring 6 make a pair, and one ball 7 as a torque transmission element rolls on each of the ball tracks constituted by the pair of track grooves 14 and 16. Incorporated as possible. The ball 7 is interposed between the track groove 14 of the joint outer ring 5 and the track groove 16 of the joint inner ring 6 to transmit torque. The cage 8 is slidably interposed between the joint outer ring 5 and the joint inner ring 6, and is fitted to the inner spherical surface 13 of the joint outer ring 5 by the outer spherical surface 8a, and the outer spherical surface 15 of the joint inner ring 6 by the inner spherical surface 8b. Mates with. The constant velocity universal joint 3 in this case is an undercut-free type in which the outer ring track groove 14 is linear on the opening side of the mouth portion 11 and the inner ring track groove 16 is straight on the back side of the mouth portion 11. Although shown, other constant velocity universal joints such as a Rzeppa type may be used.

  Further, the opening of the mouse part 11 is closed by a boot 60. The boot 60 includes a large-diameter portion 60a, a small-diameter portion 60b, and a bellows portion 60c that connects the large-diameter portion 60a and the small-diameter portion 60b. The large-diameter portion 60a is fitted around the opening of the mouse portion 11, and is fastened by the boot band 61 in this state. Further, the small-diameter portion 60b is externally fitted to the boot mounting portion 10b of the shaft 10, and is fastened by the boot band 62 in this state.

  The hub wheel 1 includes a tube portion 20 and a wheel mounting flange 21 provided at an end portion of the tube portion 20 on the outboard side. The hole portion 22 of the cylindrical portion 20 includes a shaft portion fitting hole 22a in the middle portion in the axial direction, a tapered hole 22b on the outboard side, and a large diameter hole 22c on the inboard side. In the shaft portion fitting hole 22a, the shaft portion 12 of the joint outer ring 5 and the hub wheel 1 are coupled to each other through an uneven fitting structure M described later. A tapered portion (tapered hole) 22d is provided between the shaft portion fitting hole 22a and the large diameter hole 22c. The tapered portion 22 d is reduced in diameter toward the shaft end side of the shaft portion 12 of the joint outer ring 5. The taper angle θ2 (see FIG. 8) of the taper portion 22d is, for example, 15 ° to 75 °.

  On the outer peripheral surface of the hub wheel 1 on the inboard side, a step portion 23 having a small diameter is formed. An inner member having double-row inner raceways (inner races) 28 and 29 is formed by fitting the inner ring 24 to the stepped portion 23. Of the double-row inner raceway surfaces, the outboard side inner raceway surface 28 is formed on the outer peripheral surface of the hub wheel 1, and the inboard side inner raceway surface 29 is formed on the outer peripheral surface of the inner ring 24. The wheel bearing 2 is disposed on the outer diameter side of the inner member, the inner member, and an outer member 25 having double-row outer raceways (outer races) 26 and 27 on the inner periphery, and the outer member 25. Between the outer raceway surface 26 on the outboard side and the inner raceway surface 28 of the hub wheel 1, and between the outer raceway surface 27 on the inboard side of the outer member 25 and the inner raceway surface 29 of the inner ring 24. And a ball as the rolling element 30. Since the hub ring 1 and the inner ring 24 press-fitted into the outer periphery of the hub ring 1 constitute an inner member having the inner raceways 28 and 29, the wheel bearing device can be reduced in weight and size. Seal members S1 and S2 are attached to both openings of the outer member 25.

  The wheel bearing 2 has a structure in which a cylindrical end portion on the inboard side of the hub wheel 1 is swaged and a preload is applied to the inside of the bearing by pressing the inner ring 24 with a swaged portion 31 formed by swaged. is there. Thereby, the inner ring 24 can be fixed to the hub ring 1. When preload is applied to the bearing 2 by the crimped portion 31 formed at the end of the hub wheel 1, it is not necessary to apply preload at the mouth portion 11 of the joint outer ring 5. Therefore, the shaft portion 12 of the joint outer ring 5 can be press-fitted without considering the amount of preload, and the connectivity (assembleability) between the hub wheel 1 and the joint outer ring 5 can be improved. In this case, the mouse part 11 can be brought into non-contact with the end part of the hub wheel 1 (the caulking part 31 in this embodiment). Correspondingly, a gap 98 is provided between the caulking portion 31 of the hub wheel 1 and the back surface 11 a of the mouse portion 11. By making the mouse part 11 and the hub wheel 1 non-contact, generation | occurrence | production of the noise by both contact can be prevented.

  As shown in FIG. 42, the caulking portion 31 of the hub wheel 1 and the back surface 11a of the mouse portion 11 may be brought into contact with each other. In this case, since the shaft portion 12 of the joint outer ring 5 is positioned, the dimensional accuracy of the wheel bearing device is stabilized, and the axial length of the concave-convex fitting structure M is stabilized to improve torque transmission. Can be planned. When the caulking portion 31 of the hub wheel 1 and the back surface 11a of the mouse portion 11 are brought into contact with each other in this way, it is desirable that the contact surface pressure between them is 100 MPa or less. If the contact surface pressure exceeds 100 MPa, there will be a difference in the torsional amount between the joint outer ring 5 and the hub wheel 1 when a large torque is applied, and this difference may cause a sudden slip at the contact portion and generate noise. It is. Therefore, by setting the contact surface pressure to 100 MPa or less, it is possible to provide a quiet wheel bearing device that prevents the generation of abnormal noise.

  Bolt mounting holes 32 are provided in the flange 21 of the hub wheel 1, and hub bolts 33 for fixing the wheel and brake rotor to the flange 21 are mounted in the bolt mounting holes 32. The hub wheel 1 is not provided with the pilot portion 165 provided in the hub wheel of the conventional wheel bearing device shown in FIG.

  As shown in FIGS. 2A and 2B, the concave-convex fitting structure M includes, for example, a plurality of convex portions 35 provided in the outer peripheral surface of the end portion on the outboard side of the shaft portion 12 and extending in the axial direction. A plurality of recesses 36 are formed in the inner diameter surface of the hole portion 22 of the hub wheel 1 (in the present embodiment, the inner diameter surface 37 of the shaft portion fitting hole 22a). The convex portion 35 and the concave portion 36 are tight-fitted over the entire circumference.

  In this case, as shown in FIG.2 (b), each convex part 35 is the triangle shape (mountain shape) in which the cross section has a convex round-shaped top part, The fitting area | region with the recessed part of each convex part 35 is A range A shown in FIG. Each convex part 35 and the recessed part 36 are fitted in the range from the middle part to the top part on both sides in the circumferential direction of the convex part 35 in the cross section. A gap 40 is formed between the adjacent convex portions 35 in the circumferential direction on the inner diameter side than the inner diameter surface 37 of the hub wheel 1.

  As shown in FIG. 5A, the convex portion 35 has a corner portion 39 having no roundness at the edge of the end surface 35a on the press-fitting start side. Here, the “corner portion 39” means a mountain-shaped ridge formed by the end surface 35a and the side surface 35b of the convex portion 35 intersecting (side formed by two adjacent surfaces of the polyhedron intersecting). Therefore, C-chamfered corners are excluded, but even if it is recognized that there is no C-chamfer with the naked eye, a C-chamfered shape is formed if observed microscopically. May be allowed. In addition, the corners are assumed to be “unrounded”. However, even if the corners cannot be confirmed with the naked eye, it may be recognized that an R chamfer is formed microscopically. In view of the above circumstances, in the present invention, a corner where an R chamfer of 0.1 mm or less or a C chamfer of 0.1 mm or less is formed is included in the “corner without roundness”. For example, when the male spline 41 having 58 teeth is configured with the module 0.48, in the case of R chamfering, it is about R0.02 to 0.05 mm, and in the case of C chamfering, about C0.02 to 0.05 mm. Include things in the “round corners”. Here, the module is a pitch circle diameter divided by the number of teeth.

  As the convex portion 35, a convex portion having a flat surface 44 as shown in FIG. 5B can be used.

The shape of the convex part 35 is managed based on the following dimension management targets (1) and (2) in the concave-convex fitting portion.
(1) Object of First Dimension Management As shown in FIG. 6, the top of the convex portion 35 (the male spline 41 of the male spline 41 is centered on the axis in the axially perpendicular section of the shaft portion 12 at the press-fitting start side end of the convex portion 35. The diameter D1 of the circle passing through the tooth tip 41a) and the diameter D2 (X) of the circle passing through the top of the convex portion with the axis centered at an axial cross section at an arbitrary position X in the axial direction excluding the press-fitting start side end And set to
(2) Object of second dimension management As shown in FIG. 7A, an intermediate portion in the height direction of the convex portion 35 is centered on the shaft center in a cross section perpendicular to the shaft portion 12 at the press-fitting start side end portion. The circumferential thickness L1 of the convex portion 35 on the passing reference circle C0 (circle having a diameter D3) and the reference circle C0 in a cross section perpendicular to the axis of the shaft portion 12 at the position X as shown in FIG. Is set to the circumferential thickness L2 (X) of the convex part on the circle C1 projected.

  Here, X is defined as the axial distance from the end of the convex portion 35 on the press-fitting start side, and D2 (X) and L2 (X) are the prescribed circles at the position X defined in this way. It is a function which each shows the diameter of this, and the circumferential thickness of the said prescription | regulation.

And if the object of the first dimension management and the object of the second dimension management are strictly managed too much, the processing cost of the convex portion 35 may be unduly increased. The following allowable values are given to the difference value between D1 and D2 (X) obtained and the difference value between L1 and L2 (X) obtained from the second dimension management target. I have to.
−0.2 mm ≦ D1-D2 (X) ≦ 0.2 mm (i)
−0.1 mm ≦ L1-L2 (X) ≦ 0.1 mm (ii)
However, it is assumed that 0 <X.

  In addition, said relational expression (i) and (ii) shall be materialized in all the positions of the axial direction of an uneven | corrugated fitting site | part. At this time, in the case where unevenness due to inevitable minute scratches or the like is formed in a very partial region of the uneven engagement portion, this is allowed. Further, the centers of the circle with the diameter D1 and the circle with the diameter D2 (X) are on the axis of the shaft portion 12. Further, the circumferential thicknesses L1 and L2 (X) of the convex portion 35 are managed by OPD measurement. The diameter D1 and the circumferential thickness L1 are not taken into consideration when chamfering such as C chamfering or R chamfering is performed on the corner portion of the end surface of the convex portion 35 on the press-fitting start side, and the convex portion shape is determined on the press-fitting start side. Suppose that it determines based on the top part of the convex part 35 when it assumes that it extended to the end surface, and the circumferential direction thickness.

  As shown in FIG. 1, a retaining structure M <b> 1 is provided between the end of the shaft portion 12 of the joint outer ring 5 and the inner diameter surface 37 of the hub wheel 1 to restrict the shaft portion from coming off. The retaining structure M1 includes a tapered locking piece 65 that extends from the end of the shaft portion 12 of the joint outer ring 5 to the outboard side and engages with the tapered hole 22b in the axial direction. The tapered locking piece 65 is a ring-shaped body whose diameter increases from the inboard side to the outboard side, and at least a part of the outer peripheral surface 65a is in pressure contact with or in contact with the tapered hole 22b.

  In this wheel bearing device, the foreign matter intrusion preventing means W for the concave / convex fitting structure M is provided on the inboard side and the outboard side of the concave / convex fitting structure M, respectively.

  On the inboard side, as shown in FIG. 1, a seal member 99 is fitted into a gap 98 between the caulking portion 31 of the hub wheel 1 and the back surface 11 a of the mouth portion 11. Side foreign matter intrusion prevention means W1 is configured. The gap 98 is formed from the space between the caulking portion 31 of the hub wheel 1 and the back surface 11 a of the mouth portion 11 to the space between the large-diameter hole 22 c of the hub wheel 1 and the shaft portion 12. In this way, the seal member 99 is disposed at the corner portion of the gap 98, that is, at the boundary portion between the caulking portion 31 and the large diameter portion 22c of the hub wheel 1, and the end portion of the hub wheel 1 and the bottom portion of the mouth portion 11 are arranged. By closing the gap 98 therebetween, it is possible to prevent rainwater and foreign matter from entering the concave-convex fitting structure M from the gap 98. As the sealing member 99, for example, a commercially available O-ring as shown in FIG. 11A can be used. Any seal member 99 can be used as long as it can be interposed between the end portion of the hub wheel 1 and the bottom portion of the mouth portion 11, and other than the O-ring, for example, as shown in FIG. Something like a gasket can also be used.

  The foreign substance intrusion prevention means W2 on the outboard side shown in FIG. 1 is composed of a tapered locking piece 65 as an engaging portion and a sealing material (not shown) interposed between the inner diameter surface of the tapered hole 22b. Can do. In this case, the sealing material is applied to the tapered locking piece 65. That is, a sealing material made of various resins that can be cured after application and can exhibit sealing performance between the tapered locking piece 65 and the inner diameter surface of the tapered hole 22 b may be applied to the tapered locking piece 65. In addition, as this sealing material, the thing which does not deteriorate in the atmosphere where this wheel bearing apparatus is used is selected.

  A sealing material may be interposed between the convex portion 35 and the concave portion 36, whereby the foreign matter intrusion prevention means W (W3) may be configured. In this case, a sealing material made of various resins that can be cured after application and exhibit sealing properties between the fitting contact portions 38 may be applied to the surface of the convex portion 35.

  The uneven fitting structure M can be obtained by the following procedure.

  First, a male spline having a large number of teeth extending in the axial direction on the shaft portion 12 of the joint outer ring 5 using plastic processing (rolling processing, pressing, etc.) such as rolling or pressing in this embodiment. 41 is formed. As shown in FIG. 2 (b), in the male spline 41, a circle surrounded by the tooth bottom 41 b, the tooth tip 41 a, and a region surrounded by both side surfaces connected to the tooth tip 41 a becomes the convex portion 35. The male spline 41 may be formed by using a processing method such as cutting other than the convex plastic processing.

  The male spline 41 has a module of 0.5 or less, and preferably has a smaller tooth than a normally used spline module. As a result, the moldability of the spline 41 can be improved, and the press-fit load when the male spline 41 is press-fitted into the shaft portion fitting hole 22a of the hub wheel 1 can be reduced. By forming the convex portion 35 of the shaft portion 12 with the male spline 41, it is possible to utilize processing equipment for forming a spline on this type of shaft, and the convex portion 35 can be formed at low cost. is there.

  Next, the end surface on the press-fitting start side of the convex portion 35 is finished by cutting. This cutting process is desirably performed using a parting tool as a cutting tool, whereby a sharp process can be performed and burrs are hardly generated. In particular, when the convex portion 35 is formed by plastic working, the end portion on the press-fitting start side may have an irregular shape due to the occurrence of sagging peculiar to plastic deformation. As an example thereof, FIG. 3 shows a state in which the end portion 35d has an irregular shape as a result of the plastic flow occurring in the axial direction toward the end surface on the press-fitting start side of the convex portion 35. That is, the end surface 351 of the end portion 35d is inclined toward the press-fitting start end side toward the radially outer side, and the end peripheral surface 352 is reduced in diameter toward the end surface. In addition, depending on the situation, the end surface on the press-fitting start side may incline to the opposite side to the press-fitting direction as it goes radially outward, or the end peripheral surface may expand toward the end surface. When the end 35d on the press-fitting start side of the convex portion 35 has an irregular shape as described above, it is difficult to obtain a high cutting action by the end edge when press-fitting into the hole portion 22 of the hub wheel 1 and the convex portion 35. As a result, the moldability of the concave portion 36 is deteriorated, the press-fitting load is increased, and in some cases, the convex portion 35 may be chipped.

  On the other hand, in the illustrated embodiment, as shown in FIG. 4, the end surface on the press-fitting start side of the convex portion 35 is finished by cutting, thereby removing the distorted end portion 35 d indicated by hatching in the drawing. As a result, as shown in FIG. 5B, corner portions 39 that are not round and can be cut into the other can be formed on the press-fitting start side end face. Due to the non-round corner portion 39, when the hub wheel 1 is press-fitted into the hole portion 22, a high cutting action can be obtained and the press-fit load can be kept low. The range of the end portion to be removed for finishing the end face on the press-fitting start side is determined so that the irregular portion can be removed and the length of the convex portion 35 necessary for the function of the concave-convex fitting structure M is maintained. It is desirable that the length is 3 mm or more in the axial direction.

  And in this embodiment, after finishing the press-fitting start side end surface of the convex part 35 by cutting in this way and removing the distorted end part 35d, the shape of the convex part 35 is the above relational expression (i ) And (ii). In other words, the influence of the sag of the press-fitting start side end peculiar to the plastic working is reduced as much as possible by forming the protrusion 35 in advance excessively long and cutting and removing the sag. Thus, the shape of the convex portion 35 is managed so as to satisfy the above relational expressions (i) and (ii). Moreover, the height direction dimension of the top part of the convex part 35 is satisfy | filling said relational expression (i) by grind | polishing and cutting the top part of the convex part 35 as needed. Thus, if the above relational expressions (i) and (ii) are satisfied, the height direction dimension between the different convex portions 35 becomes substantially constant, and any one of the plurality of convex portions 35 is included. Even when the projection 35 is taken, the circumferential thickness (tooth thickness) is substantially constant over the axial direction. Therefore, even if the convex portion 35 is press-fitted into the hole portion 22 of the hub wheel 1, the change in the shape of the convex portion 35 becomes as small as possible between the convex portions 35 and in the axial direction of the individual convex portions 35. In addition, it is possible to effectively prevent the expansion of the hub wheel 1 and the occurrence of the adhesion failure of the concave-convex fitting structure M. Therefore, since the expansion of the hub wheel 1 can be reliably prevented, the durability of the bearing device can be improved. In addition, since the adhesion of the concave-convex fitting structure M can be sufficiently ensured, sufficient strength can be ensured. In order to enjoy such an effect more reliably, it is preferable that | D1-D2 (X) | is 0.1 mm or less, and | L1-L2 (X) | The following is preferable. Furthermore, it is more preferable that both | D1-D2 (X) | and | L1-L2 (X) | are both in the preferable range.

  In addition, if the above relational expressions (i) and (ii) are not satisfied, such operational effects cannot be enjoyed. That is, when D1-D2 (X) is smaller than −0.2 mm, the other portion that is press-fitted into the hole portion 22 later than the convex portion 35 at the end of the convex portion 35 on the press-fitting start side. The convex portion 35 in FIG. In this case, the hole 22 of the hub wheel 1 is pushed to the outer diameter side by the subsequent protrusion 35 more than the hub wheel 1 is cut at the end of the protrusion 35 on the press-fitting start side, and the hub wheel 1 is expanded. There is a risk. Moreover, if D1-D2 (X) exceeds 0.2 mm, the convex part 35 in the edge part by the side of the press injection of the convex part 35 will be pressed into the hole part 22 later, and the convex part 35 in the other part. It will protrude too much to the outer diameter side. In this case, if the hub wheel 1 is cut at the end of the convex portion 35 on the press-fitting start side, the cut portion becomes too large, and there is a possibility that sufficient radial adhesion cannot be ensured with the subsequent convex portion 35. is there.

  Similarly, when L1−L2 (X) is smaller than −0.1 mm, the other portions that are press-fitted into the hole portion 22 later than the convex portion 35 at the end portion of the convex portion 35 on the press-fitting start side. The circumferential thickness (tooth thickness) of the convex portion 35 in the portion is too large. In this case, the hub wheel 1 is pushed so that the hole 22 of the hub wheel 1 is expanded in the circumferential direction by the subsequent protrusion 35 more than the hub wheel 1 is cut at the press-fitting start end of the protrusion 35. There is a possibility that the wheel 1 may expand. Moreover, if L1-L2 (X) exceeds 0.1 mm, the circumferential thickness of the convex portion 35 at the end of the convex portion 35 on the press-fitting start side is press-fitted into the hole portion 22 later. It becomes too larger than the convex part 35 in a part. In this case, if the hub wheel 1 is cut at the end of the convex portion 35 on the press-fitting start side, the cut portion becomes too large, and the gap between the convex portion 35 at the other portion that is press-fitted into the hole portion 22 later. Therefore, there is a possibility that sufficient circumferential adhesion cannot be secured.

  Further, as shown by cross hatching in FIG. 8, a thermosetting treatment is performed on the outer diameter surface of the shaft portion 12 to form a hardened layer H. The hardened layer H is continuously formed in the circumferential direction including the entire convex portion 35 and the tooth bottom 41b. In addition, the axial formation range of the hardened layer H is a range including at least a continuous region from the edge on the outboard side of the male spline 41 to the inner diameter portion of the bottom wall of the mouth portion 11 of the joint outer ring 5. To do. As the thermosetting treatment, various heat treatments such as induction hardening and carburizing and quenching can be employed. Here, induction hardening is a hardening method that applies the principle of heating a conductive object by placing Joule heat in a coil through which high-frequency current flows, and generating Joule heat by electromagnetic induction. is there. In addition, carburizing and quenching is a method in which carbon is infiltrated / diffused from the surface of a low carbon material and then quenched.

  On the other hand, the inner diameter side of the hub wheel 1 is maintained in an unburned state. That is, the inner diameter surface 37 of the hole portion 22 of the hub wheel 1 is an uncured portion (unburned state) that is not subjected to thermosetting. The hardness difference between the hardened layer H of the shaft portion 12 of the joint outer ring 5 and the uncured portion of the hub wheel 1 is 20 points or more in HRC. For example, the hardness of the hardened layer H is about 50 HRC to 65 HRC, and the hardness of the uncured portion is about 10 HRC to about 30 HRC. Of the inner diameter surface 37 of the hub wheel 1, it is sufficient that at least the inner diameter surface 37 of the shaft portion fitting hole 22 a is an uncured portion, and the other inner diameter surface may be subjected to thermosetting treatment. Further, if the hardness difference is ensured, the region to be the “uncured portion” may be subjected to a heat curing treatment.

  At this time, the intermediate portion in the height direction of the convex portion 35 is made to correspond to the position of the inner diameter surface 37 of the shaft portion fitting hole 22 of the hub wheel 1 before the concave portion is formed. That is, as shown in FIG. 8, the inner diameter dimension D4 of the inner diameter surface 37 of the shaft fitting hole 22a is set to the maximum outer diameter dimension of the convex portion 35 of the male spline 41 (the circumscribed circle passing through the tooth tip 41a of the male spline 41). It is set to be smaller than the diameter dimension D5 and larger than the diameter dimension D6 of the circle connecting the bottom of the male spline 41 (D6 <D4 <D5). In this case, as shown in FIG. 5 (b), the non-rounded corner portion 39 is disposed in a portion of the edge 35a of the convex portion 35 where the concave portion 36 is formed (the shaft fitting hole 22a). A non-round corner 39 is formed on the outer diameter side of the inner diameter surface 37). Of the edge of the end surface 35a of the convex portion 35, a roundness may be formed in a region on the inner diameter side of the inner diameter surface of the shaft portion fitting hole 22a.

  As shown in FIG. 8, a short cylindrical portion 66 for forming the tapered locking piece 65 is formed on the end surface 12 a of the shaft portion 12 so as to protrude from the outer peripheral edge portion along the axial direction. An outer diameter D7 of the short cylindrical portion 66 is set smaller than an inner diameter D4 of the fitting hole 22a of the hole 22. As will be described later, the short cylindrical portion 66 functions as an alignment member at the time of press-fitting the shaft portion 12 into the hole portion 22 of the hub wheel 1.

  Next, a seal member 99 such as an O-ring is externally fitted to the base portion (mouse portion side) of the shaft portion 12 of the joint outer ring 5, and the shaft center of the hub wheel 1 and the shaft center of the joint outer ring 5 of the constant velocity universal joint 3 are , The shaft portion 12 of the joint outer ring 5 is press-fitted into the hole portion 22 of the hub wheel 1. At this time, a seal material is previously applied to the outer diameter surface of the outboard side region including the male spline portion 41 and the short cylindrical portion 66 in the shaft portion 12. As described above, since the tapered portion 22d having a diameter reduced along the press-fitting direction is formed in the hole portion 22 of the hub wheel 1, the tapered portion 22d is provided with the hub ring hole portion 22 and the shaft portion 12 at the start of press-fitting. Perform centering. Further, since the inner diameter dimension D4 of the shaft portion fitting hole 22a, the maximum outer diameter dimension D5 of the convex portion 35, and the minimum outer diameter dimension D6 of the tooth bottom of the male spline 41 are as described above, the shaft portion 12 Is inserted into the shaft fitting hole 22a of the hub wheel 1 so that the convex portion 35 bites into the inner diameter portion of the end face on the inboard side of the hub wheel 1 and cuts the meat of the hub wheel 1. By pushing the shaft portion 12 forward, the inner diameter surface 37 of the shaft portion fitting hole 22 a of the hub wheel 1 is cut out or extruded by the convex portion 35, and the shape corresponding to the convex portion 35 of the shaft portion 12 is formed on the inner diameter surface 37. A recess 36 is formed. At this time, since the rounded corner portion 39 is formed at the edge of the end surface 35a of the convex portion 35, the hub wheel 1 is smoothly cut by the convex portion 35, and an increase in press-fit load can be prevented. . Further, since the hardness of the convex portion 35 of the shaft portion 12 is 20 points or more higher than the inner diameter surface 37 of the shaft portion fitting hole 22a of the hub wheel 1, it is easy to form a recess on the inner diameter surface 37 of the hub wheel 1. It becomes. Moreover, the torsional strength of the shaft portion 12 can be improved by increasing the hardness of the shaft portion side.

Through this press-fitting step, as shown in FIGS. 2A and 2B, the convex portion 3 of the shaft portion 12 is obtained.
5, a recess 36 is formed that fits into it. As the convex portion 35 bites into the inner diameter surface 37 of the hub wheel 1, the hole portion 22 is slightly expanded in diameter, and the convex portion 35 is allowed to move in the axial direction. On the other hand, if the movement in the axial direction stops, the inner diameter surface 37 is reduced in diameter to return to the original diameter. In other words, when the convex portion 35 is press-fitted, the hub wheel 1 is elastically deformed in the outer diameter direction, and a preload corresponding to the elastic deformation is applied to the surface of a portion of the convex portion 35 that fits the concave portion 36. For this reason, the recessed part 36 closely_contact | adheres to the surface of the convex part 35 over the whole axial direction. Thereby, the concave-convex fitting structure M is configured. Since a sealing material is interposed in the fitting portion 38 of the convex portion 35 and the concave portion 36, it is possible to prevent foreign matter from entering the fitting portion 38.

  Further, as the shaft portion 12 is press-fitted, plastic deformation occurs on the hub wheel 1 side, so that work hardening occurs on the surface of the recess 36. For this reason, the inner diameter surface 37 of the hub wheel 1 on the concave portion 36 side is hardened, and the rotational torque transmission can be improved.

  As shown in FIG. 8, the tapered portion 22 d can function as a guide when starting press-fitting of the shaft portion 12. Therefore, the shaft portion 12 of the joint outer ring 5 can be pressed into the hole portion 22 of the hub wheel 1 without causing misalignment. Further, since the outer diameter D7 of the short cylindrical portion 66 is set smaller than the inner diameter D4 of the fitting hole 22a of the hole portion 22, the short cylindrical portion 66 can be functioned as an alignment member, and misalignment can occur. It is possible to press-fit the shaft portion 12 into the hub wheel 1 while preventing the above-described problem, and more stable press-fitting is possible.

  As shown in FIG. 1, the concave / convex fitting structure M is required to be disposed so as to avoid the inner diameter side of the raceway surfaces 26, 27, 28, and 29 of the bearing 2 as much as possible. In particular, it is desirable to avoid the inner diameter side of the intersection with the line through which the contact angle passes on the inner races 28 and 29, and to form the concave / convex fitting structure M in the axial region between these intersections. Thereby, generation | occurrence | production of the hoop stress in a bearing raceway surface can be suppressed. Therefore, it is possible to prevent bearing failures such as a decrease in rolling fatigue life, occurrence of cracks, and stress corrosion cracking, and a high-quality bearing can be provided.

  As shown in FIG. 33 and the like, when the shaft portion 12 of the joint outer ring 5 is press-fitted into the hole portion 22 of the hub wheel 1, a step surface G is provided on the outer diameter surface of the mouth portion 11 of the joint outer ring 5, A press-fitting load (axial load) may be applied from the press-fitting jig K to the step surface G by engaging the press-fitting jig K indicated by a line with the step surface G. The stepped surface G may be provided on the entire circumference in the circumferential direction or at a predetermined pitch along the circumferential direction. The press-fitting jig to be used only needs to be able to apply an axial load corresponding to the shape of these stepped surfaces G.

  As shown in FIG. 9, in a state where the shaft portion 12 of the joint outer ring 5 and the hub wheel 1 are integrated via the concave-convex fitting structure M, the short cylindrical portion 66 protrudes from the fitting hole 22a to the outboard side. To do.

  The short cylindrical portion 66 is plastically deformed in the diameter expansion direction using a jig 67. The jig 67 includes a columnar main body 68 and a truncated cone 69 connected to the tip of the main body 68. The frustoconical portion 69 of the jig 67 has an inclined surface 69a whose inclination angle is substantially the same as the inclination angle of the tapered hole 22b, and whose outer diameter is the same as or slightly shorter than the inner diameter of the short cylindrical portion 66. The dimension is set to be smaller than the inner diameter of the portion 66. A load in the direction of arrow α is applied by fitting the truncated cone portion 69 of the jig 67 from the outboard side through the tapered hole 22b, and as a result, as shown in FIG. Gives direction expansion force. At this time, the short cylindrical portion 66 is plastically deformed to the outer diameter side by the truncated cone portion 69 of the jig 67 and is pressed against the inner diameter surface of the tapered hole 22b. Along with this, the sealing material previously applied to the outer diameter surface of the short cylindrical portion 66 is brought into close contact with the inner diameter surface of the tapered hole 22b, thereby constituting the foreign matter intrusion prevention means W2. Further, the plastically deformed short cylindrical portion 66 becomes a tapered locking piece 65 that engages with the inner diameter surface of the tapered hole 22b, and constitutes a retaining structure M1 of the shaft portion 12. In addition, when applying the load in the direction of the arrow α by the jig 67, a part of the hub wheel 1, the constant velocity universal joint 3 and the like may be supported by a fixing member (not shown) to receive the load. The inner cylindrical surface of the short cylindrical portion 66 may have a tapered shape that expands toward the shaft end. With such a shape, the inner diameter surface of the shaft portion 12 can be formed by forging, which leads to cost reduction.

  Further, in order to reduce the load of the jig 67 in the direction of the arrow α, the short cylindrical portion 66 may be notched, and the conical surface of the truncated cone portion 69 of the jig 67 is partially arranged in the circumferential direction. Things can be used. When the short cylindrical portion 66 is notched, the short cylindrical portion 66 can be easily expanded in diameter. Further, in the case where the conical surface of the truncated cone part 69 of the jig 67 is partially arranged in the circumferential direction, a part where the diameter of the short cylindrical part 66 is enlarged becomes a part on the circumference. The indentation load can be reduced.

  In the concave / convex fitting structure M described above, since the entire fitting portion 38 of the convex portion 35 and the concave portion 36 is in close contact with each other, there is no gap between the radial direction and the circumferential direction. For this reason, all the fitting parts contribute to rotational torque transmission, stable torque transmission is possible, and no abnormal noise is generated.

  Further, it is not necessary to previously form a female spline or the like on the member in which the recess 36 is formed (the hub wheel 1 in the first embodiment). Therefore, the productivity is excellent and the phase alignment between the splines is not required, so that the assemblability can be improved. Furthermore, damage to the tooth surface during press-fitting can be avoided, and a stable fitting state can be maintained. Further, since the inner diameter side of the hub wheel 1 is relatively soft, the concave portion of the hub wheel 1 is fitted with the convex portion 35 of the shaft portion 12 with high adhesion. Therefore, it becomes more effective by preventing play in the radial direction and the circumferential direction.

  In particular, as shown in FIG. 5, the inner surface 37 of the hole 22 of the hub wheel 1 can be cut out or extruded by the non-rounded corner 39 provided on the convex portion 35, so that the press-fit load is increased. Can be prevented.

  As shown in FIG. 1, in the wheel bearing device described above, the tapered locking piece 65 extending from the end of the shaft portion 12 of the joint outer ring 5 to the outboard side is pressed against or brought into contact with the inner diameter surface of the tapered hole 22b. By doing so, a retaining structure M1 for the shaft portion 12 is provided between the end portion of the shaft portion 12 of the joint outer ring 5 and the inner diameter surface 37 of the hub wheel 1. With this retaining structure M1, it is possible to prevent the shaft portion 12 of the joint outer ring 5 from coming off from the hub wheel 1 to the inboard side and maintain a stable connected state. Moreover, since the retaining structure M1 is the tapered locking piece 65, conventional screw fastening can be omitted. For this reason, it is not necessary to form the screw part which protrudes from the hole part 22 of the hub wheel 1 in the shaft part 12, and while being able to achieve weight reduction, a screw fastening operation | work can be abbreviate | omitted and aiming at improvement of assembly workability | operativity. Can do. Moreover, in the tapered locking piece 65, it is only necessary to increase the diameter of a part of the shaft portion 12 of the joint outer ring 5, and the retaining structure M1 can be easily formed. The movement of the shaft portion 12 of the joint outer ring 5 to the outboard side requires a pressing force in a direction in which the shaft portion 12 is further press-fitted, and the position shift of the shaft portion 12 of the joint outer ring 5 to the outboard side is necessary. Since the bottom portion of the mouth portion 11 of the joint outer ring 5 abuts against the caulking portion 31 of the hub wheel 1 even if it is displaced in this direction, the shaft portion 12 of the joint outer ring 5 from the hub wheel 1 Will not come out.

  Further, in the wheel bearing device described above, the foreign matter intrusion prevention means W1 and W2 are provided on the inboard side and the outboard side of the uneven fitting structure M, respectively. Intrusion of rainwater and foreign matter from the side is prevented, and the adhesion between the convex portion 35 and the concave portion 36 can be stably maintained for a long period of time.

  As the convex part 35 formed in the shaft part 12, as shown in FIGS. 12 (a) to 12 (c), a part provided with a notch 53 at the top of the end face 35a on the press-fitting start side of the convex part 35 is also used. can do. 12A illustrates a notch 53 (see FIG. 13A) formed by C chamfering, and FIG. 12B illustrates a notch 53 (see FIG. 13B) formed by R chamfering. In addition, as shown in FIGS. 12C and 13C, a C-chamfered cutout 53 may be formed in one corner portion on the outer diameter side. 12 (a) and 12 (b), it is possible to form a corner portion 39 that is not rounded on both sides of the end surface 35a except for the notch 53, and in the configuration of FIG. 12 (c), Corners 39 that are not rounded on both the oblique sides and the top side excluding the cutout portion 53 can be formed. In addition to these, a corner 39 having no roundness may be formed at the edge of the notch 53.

  By providing the notch 53 in this way, it is possible to prevent damage such as chipping or deformation at the top of the end face 35a on the press-fitting start side of the convex part 35 at the time of press-fitting or the like. For this reason, the handling of the male spline 41 is facilitated, and it is not necessary to separately take a protective measure at the press-fitting start end of the convex portion 35, so that the number of management steps can be reduced and the cost can be reduced. In addition, when a quenching process for increasing the hardness of the convex portion 35 is performed, the occurrence of quenching cracks can be prevented.

  When the cutout portion 53 is provided, as shown in FIGS. 13A to 13C, the radial length a of the cutout portion 53, that is, the edge on the side opposite to the top of the cutout portion 53 from the top portion 54 of the convex portion 35. The length a in the radial direction up to 53a is Δd (the maximum outer diameter D5 of the shaft portion 12 in FIG. 8 and the inner diameter size of the shaft portion fitting hole 22a of the hub wheel 1). As a diameter difference from D4 (expressed by D5−D4)), a range of 0 <a <Δd / 2 is set. This is because, when the projection 35 is projected onto the plane of the TUVW shown in FIGS. 12A to 12C, as shown in FIGS. 13A to 13C, the inner diameter surface 37 of the hub wheel 1 is larger. It means that there is an edge 53a on the side opposite to the top of the notch 53 on the outer diameter side. In this case, since the corner portion 39 without roundness is formed on the outer diameter side with respect to the inner diameter surface 37, the inner diameter surface 37 can be cut reliably. Specifically, the radial length a of the notch 53 is preferably 0.3 mm or less. The inclination angle of C chamfering shown in FIGS. 12 (a) and 12 (c) and the radius of curvature of R chamfering shown in FIG. 12 (b) are arbitrarily set within a range satisfying the relational expression of 0 <a <Δd / 2. Can be set.

  In FIGS. 13A to 13C, the crossing angle formed by the press-fitting start side end surface 35a of the convex portion 35 and the axis in the axial section is 90 °, but as shown in FIGS. 14 and 15A. In addition, the crossing angle θ1 can be made smaller than 90 °, or θ1 can be set larger than 90 ° as shown in FIG.

  The intersection angle θ1 is desirably set in a range of 50 ° ≦ θ1 ≦ 110 °. If the crossing angle θ1 is less than 50 °, the press-fit load increases and the moldability of the concave-convex fitting structure M deteriorates. If the crossing angle θ1 exceeds 110 °, the end face 35a is excessively inclined toward the press-fitting direction. This is because the portion 35 may be chipped. More preferably, the intersection angle θ1 is set in a range of 70 ° ≦ θ1 ≦ 110 °.

  FIG. 16 shows another configuration example of the retaining structure M1. In this wheel bearing device, the shaft portion 12 is not formed with the short cylindrical portion 66 shown in FIG. 8, and the shaft portion 12 is provided with a tapered locking piece 70 protruding in the outer diameter direction at one solid end portion of the shaft portion 12. A retaining structure M1 of the portion 12 is configured.

  The tapered locking piece 70 can be formed using a jig 71 shown in FIG. The jig 71 includes a columnar body portion 72 and a cylindrical portion 73 provided continuously to the distal end portion of the body portion 72, and a wedge portion 75 is formed at the distal end of the cylindrical portion 73. When the wedge portion 75 is driven into the end portion on the outboard side of the shaft portion 12 (when a load in the direction of arrow α is applied), the outer diameter side region of the shaft end of the shaft portion 12 becomes the outer diameter as shown in FIG. Plastic deformation to the side. As a result, a tapered locking piece 70 is formed, and at least a part of the tapered locking piece 70 comes into pressure contact with or comes into contact with the inner diameter surface of the tapered hole 22b. For this reason, similarly to the tapered locking piece 65 shown in FIG. 1 and the like, it is possible to reliably prevent the shaft portion 12 from coming off from the hub wheel 1. The foreign matter intrusion preventing means W2 can be configured by interposing a sealing material between the outer diameter surface of the tapered locking piece 70 and the inner diameter surface of the tapered hole portion 22b.

  FIG. 19 shows another configuration example of the retaining structure M1. The retaining structure M <b> 1 constitutes an outer hook-shaped locking piece 76 by crimping a part of the shaft portion 12 so as to protrude in the outer diameter direction. A stepped surface 22e is interposed between the shaft portion fitting hole 22a and the taper hole 22b of the hub wheel 1, and an outer hook-shaped locking piece 76 is pressed against or brought into contact with the stepped surface 22e.

  The outer hook-shaped locking piece 76 can be formed using a jig 77 shown in FIG. The jig 77 includes a cylindrical body 78. The outer diameter D8 of the cylindrical body 78 is set larger than the outer diameter D10 of the end portion of the shaft portion 12, and the inner diameter D9 of the cylindrical body 78 is set smaller than the outer diameter D10 of the end portion of the shaft portion 12.

  For this reason, if the axial center of this jig | tool 77 and the axial part 12 of the joint outer ring | wheel 5 is match | combined and a load is added to the end surface 12a of the axial part 12 by the arrow (alpha) direction by the end surface 77a of the jig | tool 77 in this state, As shown in FIG. 21, the outer peripheral side of the end surface 12 a of the shaft portion 12 can be crushed to form an outer hook-shaped locking piece 76.

  The outer hook-shaped locking piece 76 is engaged with the stepped surface 22e in the axial direction, so that the shaft portion 12 can be securely removed from the hub wheel 1 in the same manner as the tapered locking piece 65 shown in FIG. Can be prevented. The foreign matter intrusion prevention means W2 may be configured by interposing a sealing material between the outer hook-shaped locking piece 76 and the stepped surface 22e.

  As shown in FIG. 22A, the outer hook-shaped locking piece 76 is formed continuously in an annular shape, and as shown in FIG. 22B, a plurality of outer hook-shaped locking pieces 76 are arranged in the circumferential direction. May be intermittently arranged at a predetermined pitch. The outer hook-like locking piece 76 shown in FIG. 22B can be formed by using a jig in which the pressing portions are arranged at a predetermined pitch (for example, 90 ° pitch) along the circumferential direction. .

  When the shaft portion 12 of the joint outer ring 5 is press-fitted into the hub wheel 1, as shown in FIGS. 23 and 24, the material protrudes from the recessed portion 36 by the cutting or pushing action of the protruding portion 35, and the protruding portion 45 is It is formed. The protruding portion 45 has an amount corresponding to the volume of the portion of the convex portion 35 that fits into the concave portion 36.

  If the protruding portion 45 is left unattended, it may fall off and enter the vehicle. On the other hand, as shown in FIGS. 23 and 24, if the pocket portion 50 that accommodates the protruding portion 45 is formed on the outer diameter surface of the shaft portion 12, the protruding portion 45 is curled while being curled. Since it is stored and held, it is possible to prevent the protrusion 45 from falling off and to solve the above problems.

  The pocket portion 50 can be formed, for example, by providing a circumferential groove 51 on the outer diameter surface on the outboard side of the male spline 41 of the shaft portion 12. In this case, the hardened layer H is not provided in the pocket portion 50 as shown by the cross-hatching in FIG. 25, but from the edge on the outboard side of the male spline 41 to the inner diameter portion of the bottom wall of the mouth portion 11 of the joint outer ring 5. Form up to a continuous region. In FIG. 25, the hardened layer H does not reach the pocket portion 50, but the hardened layer H may reach the pocket portion. Even in this case, no hardened layer is formed on the short cylindrical portion 66 that forms the outer hook-shaped locking piece 76.

  The pocket portion 50 can be formed by cutting, rolling, pressing, or the like on the shaft portion 12. In particular, when the pocket portion 50 is formed by cutting, it is desirable to perform the finishing together with the press-fitting start side end face of the convex portion 35. Thereby, compared with the case where both processes are performed separately, the number of processes can be reduced and manufacturing cost can be reduced. FIG. 26 shows a state in which the finishing process of the press-fitting start side end face of the convex part 35 and the cutting process for providing the pocket part 50 are simultaneously performed on the shaft part 12 on which the male spline 41 shown in FIG. 3 is formed. Show. Thereby, the corner | angular part 39 which is not round and can be cut in the other, and the pocket part 50 are formed.

  When the male spline 41 is formed by rolling or pressing after the pocket portion 50 is formed in the shaft portion 12, the end portion on the press-fitting start side of the convex portion 35 is plastically deformed as described with reference to FIG. Depending on the case, the shape may be irregular. FIG. 27 shows a state in which the end 35e has an irregular shape as a result of plastic flow in the axial direction toward the end surface on the press-fitting start side. That is, the end surface 353 of the end portion 53e is inclined toward the press-fitting start side as going radially outward, and the end peripheral surface 354 is reduced in diameter toward the end surface. In this way, when the end 35e on the press-fitting start side of the convex portion 35 has an irregular shape, as with the case shown in FIG. It is difficult to obtain the cutting action, the moldability of the concave portion 36 by the convex portion 35 is deteriorated, the press-fitting load is increased, and in some cases, the convex portion 35 may be chipped.

  On the other hand, as shown in FIG. 26, by finishing the end surface on the press-fitting start side simultaneously with the formation of the pocket portion 50, a corner portion 39 that is not round and can be cut into the other can be formed. Due to the non-round corner 39, a high cutting action can be obtained when press-fitting into the hole of the hub wheel 1, and the press-fitting load can be kept low.

  28 to 30 show other configuration examples of the retaining structure M1 for the shaft portion 12. FIG. Of these, FIG. 28 shows a retaining structure M1 using a bolt and nut connection. Specifically, a screw shaft portion 80 is connected to the shaft portion 12, a nut member 81 is screwed onto the screw shaft portion 80, and the nut member 81 is brought into contact with the stepped surface 22 e of the hole portion 22. It is. In FIG. 29, the retaining ring 85 constitutes the retaining structure M1 of the shaft portion 12. The shaft extension portion 83 is provided on the outboard side of the male spline 41, and the circumferential groove 84 is provided in the shaft extension portion 83. And a retaining ring 85 is fitted in the circumferential groove 84. FIG. 30 shows a structure M1 in which the outer diameter surface of the shaft portion and the inner diameter surface of the hub wheel are welded to form a retaining structure M1, and the outer diameter surface on the outboard side of the shaft portion 12 and the hub wheel 1 Of the holes 22, the edge of the opening on the outboard side is joined by welding.

  The retaining structure M1 of the shaft portion 12 can be omitted as shown in FIG. In this case, as shown in FIG. 32, in the circumferential groove 51, the side surface 51a on the male spline 41 side is a plane perpendicular to the axial direction, and the opposite side surface 51b is out of the groove bottom 51c. It is a taper surface which expands toward the board side. A disc-shaped flange 52 for alignment is provided on the outboard side of the side surface 51b of the circumferential groove 51.

  If the outer diameter dimension of the collar part 52 is larger than the hole diameter of the fitting hole 22a, the collar part 52 itself is press-fitted into the fitting hole 22a. At this time, if there is a misalignment, the convex portion 35 is pressed into the hub wheel 1 as it is, and the shaft portion 12 and the hub wheel 1 are brought into contact with each other in a state where the shaft center of the shaft portion 12 and the shaft center of the hub wheel 1 are not aligned. Will be linked. In order to prevent such a problem, the outer diameter D7a (see FIG. 32) of the flange 52 is set slightly smaller than the hole diameter D4 of the shaft fitting hole 22a of the hole 22, and the outer diameter surface of the flange 52 is set. A minute gap t is provided between 52 a and the inner diameter surface of the fitting hole 22 a of the hole 22. On the other hand, if the outer diameter of the flange 52 is too small than the diameter of the fitting hole 22a, it does not function for alignment. Therefore, it is preferable that the minute gap t between the outer diameter surface 52a of the flange portion 52 and the inner diameter surface of the fitting hole 22a of the hole portion 22 is set to about 0.01 mm to 0.2 mm. The outer diameter D7a of the flange 52 may be the same as the hole diameter of the fitting hole 22a.

  In this way, by providing the flange 52 for alignment with the hole 22 of the hub wheel 1 on the outboard side of the pocket 50, the protruding portion 45 in the pocket 50 protrudes toward the flange 52. Therefore, the protruding portion 45 can be stored in the pocket portion 50 more reliably. Moreover, since the flange portion 52 has a centering function, the shaft portion 12 can be press-fitted into the hub wheel 1 while preventing misalignment. For this reason, the joint outer ring 5 and the hub ring 1 can be connected with high accuracy, and stable torque transmission is possible.

  In the wheel bearing device that does not have the retaining structure M <b> 1 shown in FIG. 31, the alignment flange 52 provided on the shaft portion 12 can be omitted.

  FIG. 33 shows an embodiment in which separation between the shaft portion 12 of the joint outer ring 5 and the hub wheel 1 is allowed. In this embodiment, as shown in FIGS. 33 and 34, the hub wheel 1 includes a cylindrical portion 20 and a flange 21 provided at an end portion on the outboard side of the cylindrical portion 20. The hole portion 22 of the cylindrical portion 20 has a shaft portion fitting hole 22a in the intermediate portion in the axial direction and a taper hole 22b on the outboard side, and has an inner diameter between the shaft portion fitting hole 22a and the tapered hole 22b. An inner wall 22g protruding in the direction is provided. The shaft portion 12 of the joint outer ring 5 and the hub wheel 1 are coupled to each other through the concave / convex fitting structure M. A recessed portion 91 is provided on the end face of the inner wall 22g on the outboard side.

  The hole portion 22 has a large-diameter portion 86 on the inboard side with respect to the shaft portion fitting hole 22a, and has a small-diameter portion 88 on the outboard side with respect to the shaft portion fitting hole 22a. A tapered portion (tapered hole) 89a is provided between the large diameter portion 86 and the shaft portion fitting hole 22a. The tapered portion 89a is reduced in diameter along the press-fitting direction when the hub wheel 1 and the shaft portion 12 of the joint outer ring 5 are coupled. The taper angle θ2 of the taper portion 89a is, for example, 15 ° to 75 °. A tapered portion 89 b is also provided between the shaft portion fitting hole 22 a and the small diameter portion 88.

  In this embodiment, the concave-convex fitting portion M is configured in the same manner as described above. That is, after the convex portion 35 is formed on the shaft portion 12, the shaft portion 12 is press-fitted into the shaft portion fitting hole 22 a of the hub wheel 1, and the inner diameter surface 37 of the shaft portion fitting hole 22 a of the hub wheel 1 is A concave portion 36 is formed to closely fit with the convex portion 35.

  After the press fitting of the shaft portion 12, the bolt member 94 is screwed into the screw hole 90 of the shaft portion 12 from the outboard side. The bolt member 94 includes a flanged head portion 94a and a screw shaft portion 94b. The screw shaft portion 94b has a large-diameter base portion 95a, a small-diameter main body portion 95b, and a tip-side screw portion 95c. In this case, a through hole 96 is provided in the inner wall 22g, the shaft portion 94b of the bolt member 94 is inserted into the through hole 96, and the screw portion 95c is screwed into the screw hole 90 of the shaft portion 12. As shown in FIG. 34, the hole diameter d1 of the through hole 96 is set to be slightly larger than the outer diameter d2 of the large base portion 95a of the shaft portion 94b. Specifically, 0.05 mm <d1−d2 <0.5 mm or so. The maximum outer diameter of the screw portion 95c is set to be the same as or slightly smaller than the outer diameter of the large-diameter base portion 95a.

  Thus, by screwing the bolt member 94 into the screw hole 90 of the shaft portion 12, the flange portion 100 of the head portion 94a of the bolt member 94 comes into contact with the recessed portion 91 of the inner wall 22g. As a result, the inner wall 22g is sandwiched between the end face 92 of the shaft portion 12 on the outboard side and the head portion 94a of the bolt member 94, and the hub wheel 1 and the joint outer ring 5 are positioned in the axial direction. At the same time, as shown in FIG. 35, a pocket portion 97 is formed in a space surrounded by the outer diameter surface of the small diameter portion 12d of the shaft portion 12, the end surface of the inner wall 22g, and the small diameter portion 88 of the inner diameter surface of the hub wheel 1. .

  In FIG. 33, the inner wall 22g is clamped in the axial direction by the end face 92 of the shaft portion 12 on the outboard side and the head portion 94a of the bolt member 94, thereby positioning the hub wheel 1 and the joint outer ring 5 in the axial direction. However, for example, when the axial position of the joint outer ring 5 relative to the hub wheel 1 is managed by the axial biting depth of the convex portion 35 of the shaft portion 12 constituting the concave-convex fitting structure M. Alternatively, the end surface 92 on the outboard side of the shaft portion 12 and the inner wall 22g may be non-contact. Further, when the caulking portion 31 of the hub wheel 1 and the back surface 11a of the mouse portion 11 are brought into contact with each other (see FIG. 42), the head 94a of the bolt member 94 and the back surface 11a of the mouse portion 11 The hub wheel 1 may be clamped. Thereby, the bending rigidity of an axial direction improves, it becomes strong to bending, and the high-quality wheel bearing apparatus excellent in durability can be provided. Moreover, since the hub wheel 1 can be positioned by press-fitting by this contact, the dimensional accuracy of the wheel bearing device can be stabilized, and the axial length of the concave-convex fitting structure M can be stabilized. Torque transmission can be improved. Further, since the seal structure can be configured by this contact, the entry of foreign matter from the crimped portion 31 side can be prevented, and the fitting state of the concave-convex fitting structure M can be stably maintained for a long time.

  By interposing a sealing material (not shown) between the seating surface 100a of the bolt member 94 and the inner wall 22g, it is possible to ensure the sealing performance between the seating surface 100a and the bottom surface of the recessed portion 91 of the inner wall 22g. it can. This prevents rainwater and foreign matter from entering the concave-convex fitting structure M from the outboard side. What is necessary is just to select and apply | coat the sealing material which consists of various resin as a sealing material so that this sealing performance can be ensured.

  When the shaft portion 12 is press-fitted into the hole portion 22 of the hub wheel 1, the material scraped off or pushed out from the inner diameter surface of the hole portion 22 by the convex portion 35 becomes the protruding portion 45, as shown in FIG. The shaft portion 12 is stored in a curled state in a pocket portion 97 provided on the outer diameter side of the small diameter portion 12 d of the shaft portion 12. In this way, by providing the pocket portion 97 for storing the protruding portion 45, the protruding portion 45 can be held (maintained) in the pocket portion 97, and the protruding portion 45 can enter the vehicle outside the apparatus. There is nothing to do. As a result, the protruding portion 45 can be kept stored in the pocket portion 97, and there is no need to perform the removal processing of the protruding portion 45, and the assembly workability is improved and the cost is reduced by reducing the number of assembly work steps. be able to.

  When the joint outer ring 5 and the hub ring 1 are separated, after the bolt member 94 is removed from the state shown in FIG. 33, the pulling more than the fitting force of the concave-convex fitting structure M between the hub ring 1 and the joint outer ring 5 is pulled out. A force is applied to pull out the joint outer ring 5 from the hub wheel 1. This extraction can be performed using a jig 120 as shown in FIG. The jig 120 includes a base 121, a pressing bolt member 123 that is screwed into the screw hole 122 of the base 121, and a screw shaft 126 that is screwed into the screw hole 90 of the shaft portion 12. A through hole 124 is provided in the base 121, and the bolt 33 of the hub wheel 1 is inserted into the through hole 124, and the nut member 125 is screwed into the bolt 33. At this time, the base 121 and the flange 21 of the hub wheel 1 are overlapped, and the base 121 is attached to the hub wheel 1.

  Thus, after attaching the base 121 to the hub wheel 1, the screw shaft 126 is screwed into the screw hole 90 of the shaft portion 12 so that the base portion 126a protrudes from the inner wall 22g to the outboard side. The protruding amount of the base 126a is set longer than the axial length of the concave-convex fitting structure M. The screw shaft 126 and the pressing bolt member 123 are disposed on the same axis.

  Thereafter, the pressing bolt member 123 is screwed into the screw hole 122 of the base 121 from the outboard side, and in this state, the bolt member 123 is screwed in the direction of the arrow. At this time, since the screw shaft 126 and the pressing bolt member 123 are disposed on the same axis, the bolt member 123 presses the screw shaft 126 toward the inboard side. As a result, the joint outer ring 5 moves toward the inboard side with respect to the hub wheel 1, and the joint outer ring 5 is detached from the hub wheel 1 as shown in FIG.

  Moreover, from the state in which the joint outer ring 5 is detached from the hub wheel 1, the hub wheel 1 and the joint outer ring 5 can be connected again using, for example, a bolt member 94 shown in FIG. That is, with the base 121 removed from the hub wheel 1 in FIG. 36 and the screw shaft 126 removed from the shaft 12, the bolt member 94 in FIG. 34 is screwed into the screw hole 90 of the shaft 12 through the through hole 96. Combine. In this state, the phases of the male spline 41 on the shaft portion 12 side and the female spline 42 of the hub wheel 1 formed by the previous press fitting are matched.

  Next, in this state, the bolt member 94 is screwed into the screw hole 90. As a result, the shaft portion 12 is fitted into the hub wheel 1. At this time, if the hole portion 22 is slightly expanded in diameter, allowing the shaft portion 12 to enter in the axial direction and stopping the movement in the axial direction, the hole portion 22 is compressed to return to the original diameter. Will be diameter. As a result, similar to the previous press-fitting, the concave / convex fitting structure M in which the entire fitting portion of the convex portion 35 with the concave portion is in close contact with the corresponding concave portion 36 is formed again, and the joint outer ring 5 and the hub ring 1 are re-established. Combined. Separation and recombination of the hub wheel 1 and the joint outer ring 5 described above can be performed with the outer member 25 of the bearing 2 still attached to the knuckle of the vehicle, as shown in FIGS. it can.

  In particular, when the bolt member 94 is screwed into the screw hole 90, the base portion 95a of the bolt member 94 is in a state corresponding to the through hole 96 as shown in FIG. In addition, as shown in FIG. 34, the hole diameter d1 of the through hole 96 is set slightly larger than the outer diameter d2 of the large base portion 95a of the shaft portion 94b (specifically, 0.05 mm <d1− d2 <about 0.5 mm), the outer diameter of the base 95a of the bolt member 94 and the inner diameter of the through hole 96 constitute a guide when the bolt member 94 is screwed through the screw hole 90. The shaft portion 12 can be press-fitted into the hole portion 22 of the hub wheel 1 without misalignment. If the axial length of the through-hole 96 is too short, a stable guide function cannot be exhibited. Conversely, if the through-hole 96 is too long, the thickness dimension of the inner wall 22g becomes large, and the axial direction of the uneven fitting structure M The length cannot be secured, and the weight of the hub wheel 1 is increased. The length of the through hole 96 is determined in consideration of the above circumstances.

  As shown in FIG. 35, if a tapered portion 90a that expands toward the opening side is formed in the opening portion of the screw hole 90 of the shaft portion 12, the screw shaft 126 in FIG. 36 or the bolt member 94 in FIG. Can be easily screwed into the screw hole 90.

  In the first press-fitting (press-fitting for forming the recess 36 in the inner diameter surface 37 of the hole 22), the press-fitting load is relatively large. Therefore, when the shaft 12 is press-fitted, it is necessary to use a press machine or the like. On the other hand, in such re-pressing, since the press-fitting load is smaller than the first press-fitting load, the shaft 12 can be stably and accurately inserted into the hole of the hub wheel 1 without using a press machine or the like. 22 can be press-fitted. For this reason, the joint outer ring 5 and the hub ring 1 can be separated and connected in the field.

In the male spline 41 shown in FIGS. 2A and 2B, as an example, the pitch of the convex portions 35 and the pitch of the concave portions 36 are set to the same value. For this reason, as shown in FIG. 2B, the circumferential thickness L3 of the convex portion 35 and the groove width L4 between adjacent convex portions are substantially the same at the intermediate portion in the height direction of the convex portion 35. It has become.

  On the other hand, as shown in FIG. 38 (a), the circumferential thickness L5 of the convex portion 35 is smaller than the groove width L6 between the adjacent convex portions at the intermediate portion in the height direction of the convex portion 35. May be. In other words, at the intermediate portion in the height direction of the convex portion 35, the circumferential thickness (tooth thickness) L5 of the convex portion 35 on the shaft portion 12 side is set to the circumferential thickness of the protruding portion 43 on the hub wheel 1 side ( Tooth thickness) is smaller than L6.

  By satisfying the above relationship in each convex portion 35, the sum Σ (B1 + B2 + B3 +...) Of the circumferential thickness L5 of the convex portion 35 on the shaft 12 side is set to the circumferential thickness of the protruding portion 43 on the hub wheel 1 side. Can be set smaller than the total sum Σ (A1 + A2 + A3 +...). As a result, the shear area of the protruding portion 43 on the hub wheel 1 side can be increased, and the torsional strength can be ensured. And since the tooth thickness of the convex part 35 is small, a press-fit load can be made small and a press-fit property can be aimed at.

  In this case, it is not necessary to satisfy the relationship of L5 <L6 for all the convex portions 35 and the protruding portions 43, and the sum of the circumferential thicknesses is greater than the sum of the circumferential thicknesses of the protruding portions 43 on the hub wheel 1 side. As long as it becomes small, about the one part convex part 35 and the protrusion part 43, it can be set as L5 = L6 or L5> L6.

  In FIG. 38 (a), the convex portion 35 is formed in a trapezoidal cross section. However, as shown in FIG. 38 (b), it may be formed in an involute-shaped cross section.

  In each of the above embodiments, the case where the convex portion 35 is formed on the shaft portion side by forming the male spline 41 on the shaft portion 12 is illustrated, but conversely, FIG. 39 and FIG. As shown to a) and (b), you may form the convex part 35 in the hub ring 1 side by forming the female spline 61 in the internal-diameter surface of the hole 22 of the hub ring 1. FIG. In this case, as in the case where the male spline 41 is formed on the shaft portion 12, for example, the female spline 61 of the hub wheel 1 is subjected to a thermosetting process so that the outer diameter surface of the shaft portion 12 is not burned. Thus, the hardness of the convex portion 35 of the hub wheel 1 is made 20 points or more harder by HRC than the outer diameter surface of the shaft portion. The female spline 61 can be formed by various processing methods such as known broaching, cutting, pressing, and drawing. As the thermosetting treatment, various heat treatments such as induction hardening and carburizing and quenching can be employed. A corner 39 having no roundness is formed on the edge of the end face on the press-fitting start side of the convex part 35.

  Also in this case, the end surface on the press-fitting start side of the convex portion 35 is finished by cutting. Moreover, it is desirable to perform this cutting process by using a parting tool as a cutting tool, whereby it is possible to perform a cutting process with a small amount of burrs. When the convex portion 35 is formed by rolling or pressing, the irregular shape portion generated at the end on the press-fitting start side is removed by this finishing. Thereby, the corner | angular part 39 which is not round and can be cut into the other can be formed in the press injection start side end surface. Due to the non-rounded corner portion 39, a high cutting action can be obtained when press-fitting into the shaft portion 12, the concave portion 36 can be accurately formed by the convex portion 35, and the press-fit load can be kept low.

  Further, as shown in FIG. 40, it is desirable to provide a pocket portion 50 ′ for accommodating the protruding portion 45 ′ formed when the shaft portion 12 of the joint outer ring 5 is press-fitted into the hub wheel 1. Accordingly, the press-fitting can be performed smoothly, and it is possible to prevent the occurrence of a situation in which the fragments of the protruding portion 45 ′ move and get caught between the shaft portion 12 and the large-diameter hole 22 c of the hub wheel 1. . Moreover, even when the seal member 99 is attached to the shaft portion 12 as shown in FIG. 39 by accommodating the fragment of the protruding portion 45 ′ in the pocket portion 50 ′, the seal member 99 due to the fragment is attached. Can prevent damage.

  The pocket portion 50 ′ can be formed, for example, by providing a circumferential groove on the inner diameter surface on the inboard side of the female spline 61 in the hole portion 22 of the hub wheel 1. In this case, as shown by cross-hatching in FIG. 39, the hardened layer H is not provided in the pocket portion 50 ', but is formed from the inboard side edge of the female spline 61 to the outboard side tapered hole 22b. In FIG. 39, the hardened layer does not reach the pocket portion 50 ', but the hardened layer H may reach the pocket portion.

  FIGS. 39 and 40 show a state in which finishing processing of the press-fitting start side end surface of the convex portion 35 and cutting processing for providing a pocket portion are simultaneously performed on the hole portion 22 in which the female spline 61 is formed. Yes. Thereby, the corner | angular part 39 which is not round and can be cut in the other, and the pocket part 50 'are formed. According to this simultaneous processing, the number of steps can be reduced and the manufacturing cost can be reduced as compared with the case where both processings are performed separately.

  Thereafter, when the shaft portion 12 is press-fitted into the hole portion 22 of the hub wheel 1, the convex portion 35 on the hub wheel 1 side forms a concave portion 36 that fits the convex portion 35 on the outer peripheral surface of the shaft portion 12. The concave-convex fitting structure M is configured in which the entire fitting portion of the convex portion 35 and the concave portion 36 is in close contact. The fitting part 38 of the convex part 35 and the recessed part 36 is the range B shown in FIG.41 (b). A gap 62 is formed between the convex portions 35 that are on the outer diameter side of the outer peripheral surface of the shaft portion 12 and adjacent in the circumferential direction.

  The intermediate portion in the height direction of the convex portion 35 corresponds to the position of the outer diameter surface of the shaft portion 12 before the concave portion is formed. That is, the outer diameter dimension D11 of the shaft portion 12 is larger than the minimum inner diameter dimension D12 of the convex portion 35 of the female spline 61 (the diameter dimension of the circle passing through the tooth tip 61a of the female spline 61), and the maximum inner diameter dimension of the female spline 61. It is set smaller than D13 (diameter dimension of a circle passing through the root 6a of the female spline 61) (D12 <D11 <D13).

  Even in this case, since the protruding portion 45 ′ is formed by press-fitting, it is preferable to provide a pocket portion 50 ′ for storing the protruding portion 45 ′. Since the protruding portion 45 ′ is formed on the inboard side of the shaft portion 12, the pocket portion is provided on the inboard side with respect to the uneven fitting structure M and on the hub wheel 1 side.

  As described above, when the convex portion 35 of the concave-convex fitting structure M is provided on the inner diameter surface of the hole portion 22 of the hub wheel 1, it is not necessary to perform the thermosetting treatment on the shaft portion 12 side. The advantage that the productivity of the outer ring 5 is excellent is obtained.

  As mentioned above, although it demonstrated per embodiment of this invention, this invention is not limited to the said embodiment, A various deformation | transformation is possible, for example, the process of finishing the end surface by the side of the press injection of the convex part 35 by cutting. May be performed after the step of forming the cured layer H by subjecting the outer diameter surface of the shaft portion 12 or the inner diameter surface of the hole portion 22 to thermosetting. However, it is desirable to perform the finishing process of the end face of the convex portion 35 before the thermosetting treatment process from the standpoint of using a cutting tool that is easy to cut, has good sharpness, and does not easily generate burrs.

  Further, as the cross-sectional shape of the convex portion 35 of the concave-convex fitting structure M, in addition to the shapes shown in FIGS. 2B and 38A and 38B, a semicircular shape, a semi-elliptical shape, a rectangular shape, etc. The convex part 35 which has various cross-sectional shapes can be employ | adopted, and the area of the convex part 35, the number, the circumferential arrangement | positioning pitch, etc. can be changed arbitrarily. The convex portion 35 can also be formed of a key separate from the shaft portion 12 and the hub wheel 11.

  Further, the hole portion 22 of the hub wheel 1 may be a deformed hole such as a polygonal hole other than a circular hole, and the cross-sectional shape of the end portion of the shaft portion 12 to be inserted into the hole portion 22 may be other than a circular cross section. An irregular cross section such as a square may be used. Further, when the shaft portion 12 is press-fitted into the hub wheel 1, it is sufficient that the hardness of the end region including at least the end surface on the press-fitting start side of the convex portion 35 is higher than the hardness of the press-fitted side. It is not necessary to increase the overall hardness of 35. In FIGS. 2B and 41B, gaps 40 and 62 are formed between the spline tooth bottom and the member in which the recess 36 is formed. You may make it satisfy with the member of the side.

  You may provide the small recessed part arrange | positioned by the predetermined pitch along the circumferential direction previously in the recessed part formation surface of the member in which a recessed part is formed. The small recess needs to be smaller than the volume of the recess 36. By providing such a small concave portion, the capacity of the protruding portion 45 formed when the convex portion 35 is press-fitted can be reduced, so that the press-fit resistance can be reduced. Further, since the protruding portion 45 can be reduced, the volume of the pocket portions 50 and 50 ′ can be reduced, and the workability of the pocket portions 50 and 50 ′ and the strength of the shaft portion 12 can be improved. In addition, the shape of a small recessed part can employ | adopt various things, such as a triangle shape, semi-ellipse shape, and a rectangle, and can also set the number arbitrarily.

  As the coupling means shown in FIG. 30, a welding coupling means is used, but an adhesive may be used instead of welding. In addition to the balls, rollers can be used as the rolling elements 30 of the bearing 2. Furthermore, in the above-described embodiment, the present invention is applied to the third generation wheel bearing device. However, the present invention can be similarly applied to the first generation, second generation, and further fourth generation wheel bearing devices. it can. In addition, when press-fitting the convex portion 35, even if the side where the concave portion 36 is formed is fixed and the side where the convex portion 35 is formed is moved, the side where the convex portion 35 is formed is reversed. It may be fixed and moved on the side where the recess 36 is formed. Alternatively, both may be moved. In the constant velocity universal joint 3, the inner ring 6 and the shaft 10 may be integrated through the concave-convex fitting structure M described in each of the above embodiments.

  In the retaining structure M1 of the shaft portion 12, for example, when a retaining ring 85 as shown in FIG. 29 is used, the retaining structure M1 is not provided at the end portion of the shaft portion 12, and the root portion of the shaft portion 12 is provided. It can also be provided on the side (mouse side).

  In the embodiment shown in FIG. 33, the sealing material interposed between the seat surface 100a of the bolt member 94 that fixes the hub wheel 1 and the shaft portion 12 with the bolt and the inner wall 22g is the seat surface 100a of the bolt member 94. In addition to applying the resin on the side, the resin may be applied on the inner wall 22g side. Moreover, you may make it apply | coat resin to both the seat surface 100a side and the inner wall 22g side. When the bolt member 94 is screwed, such a sealing material is omitted if the seat surface 100a of the bolt member 94 and the bottom surface of the recessed portion 91 of the inner wall 22g are excellent in adhesion. Is also possible. For example, if the bottom surface of the recessed portion 91 is ground, the adhesiveness with the seat surface 100a of the bolt member 94 is improved, so that application of the sealing material can be omitted. As long as the adhesion is ensured, the grinding process to the recessed portion 91 can be omitted, and the forged skin and the turning finish state can be left as they are.

  Further, the shape of the pocket portions 50 and 50 ′ is not limited as long as it can accommodate (accommodate) the protruding portion 45 to be generated. Further, the capacity of the pocket portions 50 and 50 ′ is set larger than at least the expected amount of the protruding portion 45 generated.

DESCRIPTION OF SYMBOLS 1 Hub wheel 2 Bearing 3 Constant velocity universal joint 5 Joint outer ring 11 Mouse | mouth part 11a Back surface 12 Shaft part 22 Hole part 22g Inner wall 26, 27 Outer raceway surface (outer race)
28, 29 Inner raceway surface (inner race)
30 Rolling element 31 Caulking portion 35 Protruding portion 35a Convex portion end surface 35b Convex portion side surface 36 Concave portion 37 Inner diameter surface 38 Fitting portion 39 Corner portion 45 Projecting portion 50 Pocket portion 52 Gutter portion 53 Notch portion 90 Screw hole 94 Bolt member 94a Head Portion 98 Clearance 99 Seal member 100a Seat surface M Concave and convex fitting structure M1 Retaining structure

Claims (12)

An outer member having a double-row raceway surface on the inner periphery, a hub ring attached to a wheel, and an inner member having a double-row raceway surface facing the raceway surface of the outer member on the outer periphery; A wheel bearing having a rolling member and a double row rolling element interposed between the raceway surfaces of the inner member, and a constant velocity universal joint having an outer joint member, the shaft portion of the outer joint member and the hub By fitting a convex portion extending in the axial direction provided in one of the hole portions of the ring into the other, and forming a concave portion with the convex portion on the other, the convex portion and the concave portion are fitted to each other. In a wheel bearing device in which a concave-convex fitting structure in which the entire region is in close contact is configured and the shaft portion of the outer joint member and the hub wheel are combined,
A portion excluding the end surface on the press-fitting start side of the convex portion is formed by a plastic working surface, and an end surface on the press-fitting start side of the convex portion is formed by a cutting surface,
The diameter of a circle passing through the top of the convex portion with the axis centered in the cross section perpendicular to the axis at the press-fitting start side end portion of the convex portion is D1 , and the axis at an arbitrary position X in the axial direction excluding the press-fit start side end portion The diameter of a circle passing through the top of the convex portion with the axis centered in the right-angle cross section is D2 (X ), and the intermediate portion in the height direction of the convex portion with the axis centered in the axis-perpendicular section at the press-fitting start side end L 1 the circumferential thickness of the convex portion of the above reference circle passing through, the circumferential thickness of the convex portion in the circle obtained by projecting the reference circle in the axis-perpendicular cross section in the position X L2 (X) If
For each of the convex portions, | D1-D2 (X) | value in 0.2mm below, and, | wheels the value of is equal to or is 0.1mm or less | L1-L2 (X) Bearing device.   The end face on the press-fitting start side of the convex part is finished by cutting, and the edge part of the end face on the press-fitting start side is provided with a corner portion that is not round and can be cut into the other end. The wheel bearing device described.   3. A gap is formed between a tooth bottom portion between the convex portions adjacent in the circumferential direction and a protruding portion formed on the other side and facing the tooth bottom portion in the radial direction. The wheel bearing apparatus described in 1.   The convex portion is provided on the shaft portion of the outer joint member, and the hardness of at least the end portion on the press-fitting start side of the convex portion is made higher than the inner diameter portion of the hole portion of the hub wheel. The wheel bearing apparatus of any one of -3.   The wheel bearing according to any one of claims 1 to 4, wherein a pocket portion is provided in the shaft portion of the outer joint member to accommodate a protruding portion generated by forming the concave portion by the press-fitting. apparatus.   The convex portion is provided on the inner diameter surface of the hole portion of the hub wheel, and the hardness of at least the end portion on the press-fitting start side of the convex portion is higher than the outer diameter portion of the shaft portion of the outer joint member. The wheel bearing device according to any one of claims 1 to 3, wherein the wheel bearing device is a wheel bearing device.   The wheel portion according to any one of claims 1 to 3, wherein the hole portion of the hub wheel is provided with a pocket portion for accommodating a protruding portion generated by the formation of the concave portion by the press-fitting. Bearing device.   The convex portions are provided at a plurality of locations in the circumferential direction, and the thickness in the circumferential direction of the convex portions at the intermediate portion in the height direction of the convex portions is larger than the groove width between the convex portions adjacent in the circumferential direction. The wheel bearing device according to any one of claims 1 to 7, wherein the wheel bearing device is small.   The convex portions are provided at a plurality of locations in the circumferential direction, and the sum of the circumferential thicknesses of the convex portions is determined between the convex portions adjacent in the circumferential direction at an intermediate portion in the height direction of the convex portions. The wheel bearing device according to any one of claims 1 to 8, wherein the wheel bearing device is smaller than a total sum of groove widths.   10. A retaining structure for restricting retaining of the shaft portion is provided between the shaft portion of the outer joint member and an inner diameter surface of the hub wheel. The wheel bearing apparatus described in 1.   11. The uneven fitting structure is allowed to be separated by applying an axial pull-out force, and the hub ring and the shaft portion of the outer joint member are bolted via a bolt member. The wheel bearing device according to any one of the above.   The inner member is composed of the hub wheel and an inner ring that is press-fitted into the outer periphery of the inboard side end of the hub wheel, and the raceway surfaces are formed on the outer periphery of the hub wheel and the outer periphery of the inner ring, respectively. The wheel bearing device according to any one of claims 1 to 11, wherein the wheel bearing device is provided.

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