JP5579891B2 - Wheel bearing device, manufacturing method thereof, and separation method - 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 , a manufacturing method thereof, and a separation method .

  The wheel bearing device has evolved from a structure in which a double row rolling bearing called a first generation is used alone to a second generation in which a vehicle body mounting flange is integrated with an outer member. The third generation in which one inner raceway surface of the double row rolling bearing is integrally formed on the outer periphery of the hub ring integrally having a ring, and further, the constant velocity universal joint is integrated with the hub ring. 4th generation has been developed in which the other inner raceway surface of the double-row rolling bearing is integrally formed on the outer periphery of the outer joint member that constitutes.

  For example, Patent Document 1 describes what is called a third generation. As shown in FIG. 15, the wheel bearing device called the 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 includes an outer joint member 153, an inner joint member 158 disposed in the bowl-shaped portion 157 of the outer joint member 153, and the inner joint member 158 and the outer joint member 153. A ball 159 to be disposed and a holder 160 for holding the ball 159 are provided. Further, a spline portion 161 is formed on the inner peripheral surface of the center hole of the inner joint member 158, and an end spline portion of a shaft (not shown) is inserted into the center hole, and the spline portion 161 on the inner joint member 158 side The spline portion on the shaft side is engaged.

  The hub wheel 152 includes a cylindrical shaft portion 163 and the flange 151, and a short wheel and a brake rotor (not shown) are attached to the outer end surface 164 (end surface on the anti-joint side) of the flange 151. A cylindrical pilot portion 165 is provided so as to protrude. The pilot portion 165 includes a large-diameter first portion 165a and a small-diameter second portion 165b. A brake rotor is externally fitted to the first portion 165a, and a wheel is externally fitted to the second portion 165b.

  A notch 166 is provided on the outer peripheral surface of the end portion of the shaft portion 163 on the hook-shaped portion 157 side, and the inner ring 167 is fitted into the notch 166. A first inner raceway surface 168 is provided near the flange on the outer peripheral surface of the shaft portion 163 of the hub wheel 152, and a second inner raceway surface 169 is provided on the outer peripheral surface of the inner ring 167. A bolt mounting hole 162 is provided in the flange 151 of the hub wheel 152, 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 is provided with two rows of outer raceways 170 and 171 on its inner periphery, and a flange (vehicle body mounting flange) 151 on its outer periphery. Then, the first outer raceway surface 170 of the outer member 155 and the first inner raceway surface 168 of the hub ring 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 are opposed to each other. Opposed and a rolling element 172 is interposed between them.

  The shaft portion 173 of the outer joint member 153 is inserted into the shaft portion 163 of the hub wheel 152. The shaft portion 173 has a threaded portion 174 formed at the end of the ridged portion, and a spline portion 175 is formed between the threaded portion 174 and the hooked portion 157. A spline portion 176 is formed on the inner peripheral surface (inner diameter surface) of the shaft portion 163 of the hub wheel 152, and when the shaft portion 173 is inserted into the shaft portion 163 of the hub wheel 152, The spline portion 175 engages with the spline portion 176 on the hub wheel 152 side.

Then, the nut member 177 is screwed to the screw portion 174 of the shaft portion 173 protruding from the shaft portion 163, and the hub wheel 152 and the outer joint member 153 are connected. At this time, the inner end surface (back surface) 178 of the nut member 177 contacts the outer end surface 179 of the shaft portion 163, and the end surface 180 on the shaft portion side of the hook-shaped portion 157 contacts the outer end surface 181 of the inner ring 167. That is, by tightening the nut member 177, the hub wheel 152 is sandwiched between the nut member 177 and the hook-shaped portion 157 via the inner ring 167.
JP 2004340403 A

  Conventionally, as described above, the spline portion 175 on the shaft portion 173 side and the spline portion 176 on the hub wheel 152 side are engaged. For this reason, it is necessary to perform spline processing on both the shaft portion 173 side and the hub wheel 152 side, which increases the cost, and at the time of press-fitting, the spline portion 175 on the shaft portion 173 side and the spline portion 176 on the hub wheel 152 side. It is necessary to match the unevenness of the teeth. At this time, if the teeth are pressed by matching the tooth surfaces, the uneven teeth may be damaged (peeled). Moreover, if it press-fits by matching the large diameter of an uneven | corrugated tooth | gear, without matching a tooth surface, it will be easy to produce the play of the circumferential direction. As described above, when there is a backlash in the circumferential direction, the transmission performance of the rotational torque is inferior and abnormal noise may occur. For this reason, it has been difficult to establish both the damage to the concavo-convex teeth and the play in the circumferential direction when using spline fitting as in the prior art.

  By the way, in spline fitting, even if the adhesiveness between the male spline and the female spline is improved so that the play in the circumferential direction does not occur, if the driving torque is applied, the male spline and the female spline are separated. Relative displacement may occur. If such relative displacement occurs, fretting wear occurs, and the abrasion powder may cause ablation wear. As a result, there is a possibility that rattling occurs at the spline fitting site or that stable torque transmission cannot be performed.

In view of the above problems, the present invention can suppress circumferential backlash, and is excellent in connection workability between the hub wheel and the outer joint member of the constant velocity universal joint, and at the same time with the hub wheel and the constant velocity. Provided is a wheel bearing device that can be separated from an outer joint member of a universal joint, has excellent maintainability, and can transmit torque stably over a long period of time. In addition, a manufacturing method and a separation method of the wheel bearing device are provided.

A wheel bearing device according to the present invention includes a hub wheel having a flange for mounting on a wheel, an outer raceway surface disposed on the outer peripheral side of the hub wheel, an inner raceway surface facing the outer raceway surface, and the opposite. A double row rolling bearing having rolling elements arranged between the outer raceway surface and the inner raceway surface and a constant velocity universal joint having an outer joint member are unitized and inserted into the hole of the hub wheel, etc. A wheel bearing device in which a shaft portion of an outer joint member of a speed universal joint is detachably coupled to a hub wheel, and a plurality of protrusions extending in an axial direction provided on an outer diameter surface of the shaft portion of the outer joint member The hub ring is press-fitted along the axial direction into the hole inner diameter surface of the hub wheel, with the corresponding protrusions corresponding to the small recesses provided at a predetermined pitch on the inner diameter surface of the hole of the hub wheel. On the inner diameter surface of the hole, a recess is formed by cutting with the press-fitted protrusion. Constructs a concave-convex fitting structure in which the entire fitting contact area between the convex part and the concave part is in close contact, and a bolt insertion hole is provided integrally with or separate from the hub wheel, and the bolt member is screwed onto the shaft center of the shaft part The screw hole is provided, and the hub ring and the shaft portion of the outer joint member are fixed by screwing the bolt member into the screw hole through the bolt insertion hole, and the bolt member is removed from the screw hole. Separation of the hub wheel from the shaft portion of the outer joint member is allowed, and a radial clearance and a circumferential direction are provided to each convex portion at an end portion of the hub wheel hole inner diameter surface on the press-fitting start side of the convex portion. A bolt member inserted into the bolt insertion hole with a female serration-shaped shaft press-fit guide portion that can be fitted through either one or both of the gaps, with the convex portion fitted to the shaft press-fit guide portion. Can be screwed into the screw hole .

In such a configuration, a convex portion in a state of fitted into the shaft section press-fitting guide portion, the bolt member inserted into the bolt insertion hole, since the possible screwed into the screw hole, a bolt member, a bolt insertion hole By screwing into the screw hole while guiding, it is possible to form a concavo-convex fitting structure in which the convex portion is press-fitted into the concave portion and the entire fitting contact portion between the convex portion and the concave portion is in close contact.

  According to the wheel bearing device of the present invention, the concave / convex fitting structure has the entire fitting contact portion between the convex portion and the concave portion in close contact with each other. No gap is formed.

In addition, if an axial pulling force is applied to the shaft portion of the outer joint member, the outer joint member can be removed from the hole of the hub wheel. In addition, after the shaft portion of the outer joint member is pulled out from the hole portion of the hub wheel, if the shaft portion of the outer hand member is press-fitted again into the hole portion of the hub wheel, the entire fitting contact region between the convex portion and the concave portion can be obtained. It is possible to reconfigure the concave-convex fitting structure that closely contacts. Further, since the hub wheel and the shaft portion of the outer joint member are fixed via the bolt coupling means, the axial displacement of the shaft portion of the outer joint member from the hub wheel is restricted .

In this case, the bolt member is provided with a threaded portion and a non-threaded portion, and a diameter gap is provided between the bolt insertion hole and the non-threaded portion of the bolt member inserted into the bolt insertion hole. It is desirable to make it smaller than the difference between the maximum diameter dimension of the shaft portion of the outer joint member and the minimum diameter dimension of the hole portion of the hub wheel in the concave-convex fitting structure. Thereby, a bolt insertion hole becomes a guide at the time of the press injection of the axial part of an outer joint member.

It is preferable to provide an inner wall for partitioning the inside of the hole of the hub wheel and to provide a bolt insertion hole in the inner wall. This inner wall improves the rigidity around the bolt insertion hole .

Further, it is preferable that the convex portion is formed by a spline including a peak portion and a valley portion, and the module of the spline is 0.5 or less .

In the wheel bearing device described above , the bolt member is removed from the screw hole to separate the hub wheel and the shaft portion of the outer joint member, and then the shaft portion serration is fitted to the shaft portion press-fitting guide portion, and the bolt insertion hole The screw member is screwed into the screw hole via the screw hole, and the bolt member is screwed into the screw hole while being guided by the bolt insertion hole, so that the shaft portion of the outer joint member is fitted into the hole portion of the hub wheel, And a convex-concave fitting structure which press-fits a convex part in a recessed part and the fitting contact site | part whole area | region of a convex part and a recessed part closely_contact | adheres can be comprised.

Further, in the wheel bearing device described above, the screw member is screwed into the screw hole, the base having the second screw hole is attached to the hub wheel, and the bolt member screwed into the second screw hole of the base is installed. By screwing, a pressing force in the axial direction can be applied to the screw shaft, and the hub wheel and the shaft portion of the outer joint member can be separated .

The wheel bearing device according to the present invention has a concave-convex fitting structure that integrates the hub ring and the shaft portion of the outer joint member of the constant velocity universal joint that is inserted into the hole of the hub ring. The play in the circumferential direction of the structure portion can be eliminated. For this reason, all of the fitting parts contribute to rotational torque transmission, stable torque transmission is possible, and no noise is generated due to looseness. If the concave portion is formed by press-fitting the convex portion into the small concave portion formed on the inner diameter surface of the hub wheel, it is possible to reduce the press-fitting resistance by reducing the capacity of the protruding portion formed when the convex portion is press-fitted. .

In addition, by applying an axial pulling force to the shaft portion of the outer joint member, the outer joint member can be removed from the hole of the hub wheel, so that the workability (maintenability) of repair and inspection of each part is improved. Improvements can be made. In addition, after the repair / inspection of each part, the shaft portion of the outer joint member is press-fitted into the hole of the hub wheel again, thereby forming a concave-convex fitting structure in which the entire fitting contact portion between the convex portion and the concave portion is in close contact. Can do.

Since the hub wheel and the constant velocity universal joint are fixed via a bolt member screwed into the screw hole, the axial disconnection of the shaft portion of the outer joint member from the hub wheel is restricted, and a stable connection state is maintained. Can

  Hereinafter, embodiments of the present invention will be described with reference to FIGS. FIG. 1 shows a wheel bearing device according to a first embodiment. This wheel bearing device is a hub wheel 1, a double row rolling bearing 2 and a constant velocity universal joint 3 integrated with each other. 1 and the shaft portion 12 of the outer joint member of the constant velocity universal joint 3 that is inserted into the hole portion 22 of the hub wheel 1 are detachably coupled via the concave-convex fitting structure M.

  The constant velocity universal joint 3 includes a plurality of outer rings 5 serving as outer joint members, an inner ring 6 serving as an inner joint member disposed on the inner side of the outer ring 5, and a plurality of torque transmissions interposed between the outer ring 5 and the inner ring 6. The ball 7 and the cage 8 that is interposed between the outer ring 5 and the inner ring 6 and holds the ball 7 are configured as main members. As shown in FIG. 8 and the like, the inner ring 6 is spline-fitted by press-fitting an end 10a of the shaft 10 into the inner diameter of the shaft hole and is coupled to the shaft 10 so that torque can be transmitted. Note that a retaining ring 9 for retaining the shaft is fitted to the end portion 10a of the shaft 10.

  The outer ring 5 is composed of a mouse part 11 and a stem part (shaft part) 12. The mouse part 11 has a bowl shape opened at one end, and a plurality of track grooves 14 extending in the axial direction are circumferentially formed on the inner spherical surface 13 thereof. It is formed at equal intervals in the direction. In the 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 outer ring 5 and the track groove 16 of the inner ring 6 make a pair, and one ball 7 as a torque transmitting element can roll on each ball track constituted by the pair of track grooves 14 and 16. It is incorporated. The ball 7 is interposed between the track groove 14 of the outer ring 5 and the track groove 16 of the inner ring 6 to transmit torque. The cage 8 is slidably interposed between the outer ring 5 and the inner ring 6, contacts the inner spherical surface 13 of the outer ring 5 at the outer spherical surface, and contacts the outer spherical surface 15 of the inner ring 6 at the inner spherical surface. The constant velocity universal joint in this case is a Zepper type, but is another constant velocity universal joint such as an undercut free type having a straight straight portion at the bottom of each track groove 14, 16. May be.

  Further, the opening of the mouse part 11 is closed by a boot 18. The boot 18 includes a large diameter portion 18a, a small diameter portion 18b, and a bellows portion 18c that connects the large diameter portion 18a and the small diameter portion 18b. The large-diameter portion 18a is externally fitted to the opening of the mouse portion 11, and is fastened by the boot band 19a in this state, and the small-diameter portion 18b is externally fitted to the boot mounting portion 10b of the shaft 10, and in this state, the boot band 19b It is concluded.

  As shown in FIGS. 1 and 6, the hub wheel 1 includes a cylindrical portion 20 and a flange 21 provided at an end portion of the cylindrical portion 20 on the opposite joint side. The hole portion 22 of the cylindrical portion 20 has a shaft portion fitting hole 22a and a tapered hole 22b on the anti-joint side, and an inner wall protruding in the inner diameter direction between the shaft portion fitting hole 22a and the tapered hole 22b. 22c is provided. That is, the shaft portion 12 of the outer ring 5 of the constant velocity universal joint 3 and the hub wheel 1 are coupled to each other through the concave-convex fitting structure M described later in the shaft portion fitting hole 22a. A concave recess 51 is provided on the end surface of the inner wall 22c on the side opposite to the shaft fitting hole.

  The hole 22 has a large-diameter portion 46 on the opening side opposite the inner wall side from the shaft portion fitting hole 22a, and a small-diameter portion 48 on the inner wall side from the shaft portion fitting hole 22a. A tapered portion (tapered hole) 49a is provided between the large diameter portion 46 and the shaft portion fitting hole 22a. The tapered portion 49a is reduced in diameter along the press-fitting direction when the hub wheel 1 and the shaft portion 12 of the outer ring 5 are coupled.

  The rolling bearing 2 includes an inner ring 24 that fits in a stepped portion 23 provided on the joint side of the tubular portion 20 of the hub wheel 1, and an outer member that is fitted over the tubular portion 20 through the inner ring 24 of the hub wheel 1. 25. The outer member 25 is provided with two rows of outer raceways (outer races) 26 and 27 on its inner circumference, and a first inner raceway (provided on the outer circumference of the first outer raceway 26 and the shaft portion of the hub wheel 1). The inner race) 28 is opposed to the second outer raceway surface 27 and the second inner raceway surface (inner race) 29 provided on the outer peripheral surface of the inner ring 24 is opposed to the ball as the rolling element 30 therebetween. Is inserted. For this reason, in this wheel bearing device, the hub ring 1 and the inner ring 24 constitute an inner member 39 of the rolling bearing 2. Seal members S1 and S2 are attached to both openings of the outer member 25.

  A knuckle 34 extending from a vehicle suspension device (not shown) is attached to the outer ring, which is the outer member 25. That is, the entire outer surface of the outer member 25 is a cylindrical surface, and the cylindrical surface 25a is a press-fitting surface into which the knuckle 34 is press-fitted. Thus, the outer member 25 can be press-fitted into the cylindrical inner surface 34a of the knuckle. In this case, it is preferable that the relative axial and circumferential displacement between the knuckle 34 and the outer member 25 is regulated by the tightening allowance between the knuckle press-fitting surface 25a and the knuckle inner diameter surface 34a. For example, when the fitting surface pressure between the outer member 25 and the knuckle 34 × the fitting area is defined as a fitting load, a value obtained by dividing the fitting load by the equivalent radial load of the rolling bearing is a creep generation limit. The design specification of the outer member 25, that is, the fitting fastening allowance between the outer member 25 and the knuckle 34 is set in consideration of the creep generation limit factor in advance.

  For this reason, it is possible to prevent the outer member 25 from slipping off in the axial direction and creeping in the circumferential direction by tightening the knuckle press-fitting surface 25a of the outer member 25 and the knuckle inner diameter surface 34a of the knuckle 34. Here, creep means that the bearing surface slightly moves in the circumferential direction due to insufficient fitting tightening allowance or poor processing accuracy of the mating surface, and the mating surface becomes mirrored, and in some cases, seizure or welding occurs with galling. Say. In addition, it is preferable that circumferential grooves are provided in the knuckle press-fitting surface 25a of the outer member 25 and the inner diameter surface 34a of the knuckle 34, and a retaining ring 59 is provided between these circumferential grooves.

  In this case, the end of the hub wheel 1 on the joint side is swaged, and the inner ring 24 is pressed toward the outboard side by the swaged portion 31 to apply preload to the bearing 2. As a result, the inner ring 24 can be fastened to the hub wheel 1. The flange 21 of the hub wheel 1 is provided with a bolt mounting hole 32, and a hub bolt 33 for fixing the wheel and the brake rotor to the flange 21 is mounted in the bolt mounting hole 32.

  The shaft portion 12 of the outer ring 5 is provided with a screw hole 50 that opens at the end surface on the anti-joint side (anti-mouse side) in the shaft center portion. The screw hole 50 is a tapered portion 50a whose opening is expanded toward the opening. A small-diameter portion 12b is provided at the end of the shaft portion 12 on the anti-joint side (anti-mouse side). That is, the shaft portion 12 includes a main body portion 12a having a large diameter and a small diameter portion 12b.

  As shown in FIGS. 2 and 3, the concave-convex fitting structure M includes, for example, a convex portion 35 provided in the shaft portion 12 and extending in the axial direction, and an inner diameter surface of the hole portion 22 of the hub wheel 1 (in this case, the shaft The inner surface 37) of the part fitting hole 22a is formed with a concave part 36, and the entire fitting contact part 38 of the convex part 35 and the concave part 36 of the hub wheel 1 fitted to the convex part 35 is in close contact. Yes. That is, a plurality of convex portions 35 are arranged at a predetermined pitch along the circumferential direction on the outer peripheral surface of the shaft portion 12 on the side opposite to the mouse portion, and the inner diameter surface of the shaft portion fitting hole 22a of the hole portion 22 of the hub wheel 1 A plurality of concave portions 36 into which the convex portions 35 are fitted to 37 are formed along the circumferential direction. That is, the convex part 35 and the concave part 36 fitted to this are tight-fitted over the entire circumference in the circumferential direction.

  In this case, each convex portion 35 has a triangular shape (mountain shape) having a convex rounded apex in cross section, and the fitting contact portion (recessed fitting portion) 38 of each convex portion 35 is shown in FIG. It is the range A shown in b), which is the range from the mid-section of the mountain in the cross section to the summit. Further, a gap 40 is formed on the inner diameter side with respect to the inner diameter surface 37 of the hub wheel 1 between the adjacent convex portions 35 in the circumferential direction.

  In this way, the hub wheel 1 and the shaft portion 12 of the outer ring 5 of the constant velocity universal joint 3 can be connected via the concave-convex fitting structure M. At this time, as described above, the end of the hub wheel 1 on the joint side is swaged, and the swaged portion 31 applies preload to the rolling bearing 2. There is no need to apply a preload to the inner ring 24.

  In this case, the bottom back surface 11a of the mouse part 11 of the outer ring 5 is brought into contact with the end surface 31a of the crimping part 31, but the bottom back surface 11a of the mouse part 11 of the outer ring 5 and the end surface 31a of the crimping part 31 are not in contact with each other. It may be a contact. That is, when the bottom rear surface 11a of the mouth portion 11 of the outer ring 5 and the end surface 31a of the crimping portion 31 are in contact with each other, there is a possibility that abnormal noise may be generated due to friction between the contact surfaces. For this reason, generation | occurrence | production of abnormal noise can be eliminated by making it non-contact. However, even in the abutted state, the noise can be set so as not to be generated depending on the abutting force, the material of the abutting surface, the finished state of the abutting surface, and the like. For this reason, in this invention, it is made to contact | abut (contact).

  In the case of contact, if the contact surface pressure between the caulking portion 31 of the hub wheel 1 and the bottom rear surface (back surface) 11a of the mouse portion 11 exceeds 100 MPa, there is a possibility of generating abnormal noise. That is, when a large torque load is applied, a difference occurs in the amount of twist between the outer ring 5 of the constant velocity universal joint 3 and the hub wheel 1, and this difference causes a sudden contact between the outer ring 5 of the constant velocity universal joint 3 and the hub wheel 1. Slip occurs and abnormal noise occurs. On the other hand, if the contact surface pressure is 100 MPa or less, it is possible to prevent a sudden slip, and to suppress the generation of abnormal noise. Thereby, a quiet wheel bearing device can be configured. Even if the contact surface pressure is 100 MPa or less, it is necessary that the contact surface pressure is not less than the surface pressure that can constitute the seal structure.

  The surface pressure of the contact portion between the outer end surface 31a of the caulking portion 31 of the hub wheel 1 and the back surface 11a of the mouth portion 11 depends on the tightening torque of the bolt member 54, but the shaft generated by the tightening torque. The force is consumed by the axial frictional force of the concave / convex fitting part and the force for further forming the concave / convex fitting part (press-fit load when forming the concave / convex fitting part), so only when more axial force is applied Contact surface pressure does not increase. Therefore, the contact surface pressure can be easily suppressed to 100 MPa or less, and no stick-slip sound is generated.

A bolt member 54 is screwed into the screw hole 50 of the shaft portion 12 from the anti-joint side. As shown in FIGS. 1 and 6, the bolt member 54 includes a flanged head portion 54a and a screw shaft portion 54b. The screw shaft portion 54b has a non-threaded portion 55a on the proximal end side and a threaded portion 55b on the distal end side. In this case, a bolt insertion hole 56 is provided in the inner wall 22 c, the shaft portion 54 b of the bolt member 54 is inserted into the bolt insertion hole 56, and the screw portion 55 c is screwed into the screw hole 50 of the shaft portion 12. As shown in FIG. 8, the hole diameter D2 of the bolt insertion hole 56 is set slightly larger than the outer diameter D1 of the non-threaded portion 55a of the shaft portion 54b. Specifically, 0.05 mm < D1 − D2 <0.5 mm. The maximum outer diameter of the threaded portion 55c is set to be the same as or slightly smaller than the outer diameter of the large base portion 55a.

  In this wheel bearing device, as shown in FIG. 2, a shaft portion press-fitting guide portion M1 that guides the press-fitting of the shaft portion 12 during press-fitting is provided on the convex portion press-fitting start side. In this case, it consists of a female spline 44 provided in the tapered portion 49 a of the hole portion 22. That is, as shown in FIG. 4 (a), the guide recess 44a has a predetermined pitch (in this case, the same pitch as the arrangement pitch of the protrusions 35) along the circumferential direction on the shaft fitting hole 22a side of the taper 49a. Is provided.

In this case, as shown in FIG. 6, the maximum outer diameter of the projections 35 of the bottom diameter D6 of the guiding recesses 44a, i.e. of a circle connecting vertexes of the projections 35 a crest 41a of the spline 41 diameter ( to be larger than the circumscribed circle diameter) D3, between the bottom of the top and the guide recesses 44a of the projections 35, as shown in FIG. 4 (a), to form a radial clearance C1.

Next, the fitting method of the uneven fitting structure M will be described. In this case, as shown in FIG. 6, the outer diameter portion of the shaft portion 12 is subjected to thermosetting treatment, and a spline 41 including a peak portion 41 a and a valley portion 41 b along the axial direction is formed on the cured layer H. For this reason, the peak portion 41a of the spline 41 is hardened, and the peak portion 41a becomes the convex portion 35 of the concave-convex fitting structure M. The spline 41 is provided on the small diameter side of the main body 12 a of the shaft 12. The range of the hardened layer H in this embodiment is from the outer end edge of the spline 41 to a part of the bottom wall of the mouth portion 11 of the outer ring 5 as shown by the cross hatched portion. As this 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. The carburizing and quenching is a method in which carbon is infiltrated / diffused from the surface of the low carbon material and then quenched. The module of the spline 41 of the shaft portion 12 is a small tooth of 0.5 or less. Here, the module is a pitch circle diameter divided by the number of teeth.

  On the inner diameter surface 37 side of the hole portion 22 of the hub wheel 1 (that is, the inner diameter surface of the shaft portion fitting hole 22a), an uncured portion (unburned state) that is not subjected to the thermosetting treatment. The hardness difference between the hardened layer H of the shaft portion 12 of the outer ring 5 and the uncured portion of the hub wheel 1 is 20 points or more in HRC. More specifically, 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 30 HRC.

At this time, the projecting direction intermediate portion of the convex portion 35 corresponds to the position of the concave portion forming surface (in this case, the inner diameter surface 37 of the shaft portion fitting hole 22a) before the concave portion is formed. That is, as shown in FIG. 6, the inner diameter dimension (hub ring inner diameter) D4 of the inner diameter surface 37 of the shaft portion fitting hole 22a is set to the maximum diameter size of the shaft portion 12 in the uneven fitting structure M , that is, the peak portion of the spline 41. 41a, which is smaller than the diameter dimension (circumferential circle diameter) D3 of the circle connecting the vertices of the convex part 35, and is the minimum diameter dimension of the valley part formed between the convex parts of the shaft part 12 , that is, the valley part 41b of the spline 41. It is set larger than the diameter dimension D5 of the circle connecting the bottoms of the two. That is, D5 <D4 <D3. Further, D3 is set smaller than the hole diameter dimension D7 of the large-diameter portion 46 of the hole 22.

  The spline 41 can be formed by various processing methods such as rolling processing, cutting processing, press processing, and drawing processing, which are known publicly known means. Moreover, various heat processing, such as induction hardening and carburizing hardening, can be employ | adopted as a thermosetting process. Note that the press-fitting start end surface 35 a of the convex portion 35 formed by forming the spline 41 is a flat surface orthogonal to the axial direction of the shaft portion 12.

Then, as shown in FIG. 6, the shaft center of the hub wheel 1 and the shaft center of the outer ring 5 of the constant velocity universal joint 3 are in a combined state. In this state, the shaft portion 12 of the outer ring 5 is inserted (press-fitted) into the hub wheel 1. That is, the projections 35 of the shaft portion 12 are fitted into the guide recesses 44a of the shaft portion press-fitting guide portion M1. Thereby, the axial center of the hub wheel 1 and the axial center of the outer ring 5 are brought into a coincident state. At this time, since the end portion of each guide recess 44a on the uneven fitting structure side is a flat surface 77a (see FIG. 2) orthogonal to the press-fitting direction, the press-fitting start end surface 35a of the convex portion 35 is received. It is possible to press fit from this state. At this time, as described above, the diameter dimension D4 of the inner diameter surface 37 of the shaft portion fitting hole 22a, the maximum diameter dimension D3 of the spline 41, and the minimum diameter dimension D5 of the spline 41 are as described above. Moreover, since the hardness of the convex portion 35 is 30 points or more larger than the hardness of the inner diameter surface 37, if the shaft portion 12 is press-fitted into the hole portion 22 of the hub wheel 1, the convex portion 35 bites into the inner diameter surface 37. Then, the convex part 35 will form the recessed part 36 with which this convex part 35 fits along an axial direction.

  This press-fitting is performed until the bottom rear surface 11a of the mouse portion 11 comes into contact with the end surface 31a of the crimping portion 31 of the hub wheel 1. At this time, as shown in FIG. 5, the end surface 52 of the small diameter portion 12b of the shaft portion 12 is maintained in a state where it does not contact the end surface 53 of the inner wall 22c. If it press-fits in this way, as shown to Fig.3 (a) (b), the whole fitting contact site | part 38 of the convex part 35 of the edge part of the axial part 12 and the recessed part 36 fitted to this will be carried out. It is in close contact. In other words, the shape of the convex portion 35 is transferred to the other-side concave portion forming surface (in this case, the inner diameter surface 37 of the shaft portion fitting hole 22a of the hole portion 22). At this time, the convex portion 35 bites into the inner diameter surface 37 of the hole portion 22, so that the hole portion 22 is slightly expanded in diameter, and the convex portion 35 is allowed to move in the axial direction. When the movement stops, the hole 22 is reduced in diameter to return to the original diameter. In other words, the hub wheel 1 is elastically deformed in the radial direction when the convex portion 35 is press-fitted, and a preload corresponding to this elastic deformation is applied to the tooth surface of the convex portion 35 (surface of the concave portion fitting portion). For this reason, the concave / convex fitting structure M in which the entire concave portion fitting portion of the convex portion 35 is in close contact with the corresponding concave portion 36 can be reliably formed. That is, a female spline 42 that closely contacts the male spline 41 is formed on the inner diameter surface of the hole 22 of the hub wheel 1 by the spline (male spline) 41 on the shaft portion 12 side.

  In this way, the concave-convex fitting structure M is configured. In this case, the concave-convex fitting structure M is disposed at a position directly below the raceway surfaces 26, 27, 28, 29 of the rolling bearing 2. Here, the direct under-position is a position that does not correspond to the radial direction with respect to the ball contact portion position of the raceway surfaces 26, 27, 28, and 29.

  After the press-fitting, the bolt member 54 is screwed into the screw hole 50 of the shaft portion 12 from the opposite joint side. Thus, by screwing the bolt member 54 into the screw hole 50 of the shaft portion 12, the flange portion 60 of the head portion 54a of the bolt member 54 is fitted into the recessed portion 51 of the inner wall 22c. As a result, the hub wheel 1 is sandwiched between the head 54 a of the bolt member 54 and the concave-convex fitting structure M, or between the head 54 a of the bolt member 54 and the bottom bottom surface (back surface) 11 a of the mouse portion 11. Thus, the hub wheel 1 and the constant velocity universal joint 3 are integrated. In this manner, the bolt coupling means M5 on the device shaft center where the hub wheel 1 and the shaft portion 12 of the outer ring 5 are coupled is constituted by the bolt member 54 and the screw hole 50 etc. into which the bolt member 54 is screwed. The

In this case, the diameter difference (diameter gap) between the hole diameter D2 of the bolt insertion hole 56 and the shaft diameter D1 of the non-threaded portion 55a of the bolt member 54 is Δd, and the maximum diameter dimension D3 of the shaft portion 12 in the uneven fitting structure M is When the diameter difference from the minimum diameter dimension D4 of the hole 22 of the hub wheel in the concave-convex fitting structure M (diameter dimension of the circle connecting the peaks of the female spline 42: see FIG. 8) is Δd2, 0 It is assumed that <Δd <Δd2.

  In this case, a sealing material (not shown) may be interposed between the seat surface 60a of the bolt member 54 and the inner wall 22c. For example, sealing materials (sealing agents) made of various resins that can be cured after application to the seating surface 60a of the bolt member 54 and exhibit sealing properties between the seating surface 60a and the bottom surface of the recessed portion 51 of the inner wall 22c. What is necessary is just to apply. In addition, as this sealing material, the thing which does not deteriorate in the atmosphere where this wheel bearing apparatus is used is selected. Further, the sealing material may be applied to the inner wall 22c side, or may be applied to the seating surface 60a side and the inner wall 22c side.

  By bringing the caulking portion 31 and the bottom bottom surface 11a of the mouth portion 11 of the outer ring 5 into contact with each other, the bending rigidity in the axial direction is improved, the bending strength is enhanced, and a high-quality product with excellent durability is obtained. Become. In addition, positioning at the time of press-fitting can be configured by this contact. As a result, the dimensional accuracy of the wheel bearing device can be stabilized, and the axial length of the concave-convex fitting structure M disposed along the axial direction can be ensured to be stable. Can be improved. Furthermore, a seal structure can be formed by this contact, foreign matter can be prevented from entering the concave-convex fitting structure M from the crimping portion 31 side, and the concave-convex fitting structure M can maintain a stable fitting state for a long period of time.

  Further, the end surface 31a of the caulking portion 31 and the bottom back surface 11a of the mouse portion 11 are in contact with each other, and the sealing material is interposed between the end surface 31a of the caulking portion 31 and the bottom back surface 11a of the mouse portion 11. (Sealant) may be interposed. In this case, the sealing material may be applied to the end surface 31a side, the sealing material may be applied to the bottom back surface 11a side, or the sealing material may be applied to the end surface 31a side and the bottom back surface 11a side.

  As described above, in the present invention, the concave-convex fitting structure M in which the entire fitting contact portion 38 between the convex portion 35 of the shaft portion 12 and the concave portion 36 of the hub wheel 1 is in close contact can be reliably formed. Moreover, it is not necessary to form a spline portion or the like on the member in which the concave portion 36 is formed, which is excellent in productivity, and does not require the phase alignment between the splines. The tooth surface can be prevented from being damaged, and a stable fitting state can be maintained.

  In the concave / convex fitting structure M, the entire fitting contact portion 38 between the convex portion 35 and the concave portion 36 is in close contact with each other. Therefore, in the fitting structure M, there is no gap in which play occurs in 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.

  Since the shaft portion press-fitting guide portion M1 is provided, when the shaft portion 12 is press-fitted into the hole 22 of the hub wheel 1, it can be press-fitted along the shaft portion press-fitting guide portion M1.

  By the way, if the shaft portion 12 is press-fitted into the hole portion 22 of the hub wheel 1, the formed protruding portion 45 is curled while being curled, as shown in FIGS. It is accommodated in a space accommodating portion 57 composed of a space provided on the diameter side. Here, the protruding portion 45 is the material of the capacity of the concave portion 36 into which the convex portion 35 is inserted (fitted), and is extruded from the concave portion 36 to be formed, and is cut to form the concave portion 36. It is comprised from what was extruded, what was extruded, and what was cut. For this reason, the protruding portion 45 which is a part of the material scraped off or pushed out from the inner diameter surface of the hole portion 22 enters the storage portion 57.

  Thus, by providing the storage portion 57 for storing the protruding portion 45 generated by forming the concave portion by the press-fitting, the protruding portion 45 can be held (maintained) in the storage portion 57, and the protruding portion 45 is outside the apparatus. Never get into any other vehicle. That is, the protruding portion 45 can be kept stored in the storage portion 57, and it is not necessary to perform the removal processing of the protruding portion 45, so that the number of assembling operations can be reduced, and the assembly workability can be improved. Cost reduction can be achieved.

  The bolt coupling means M5 restricts the axial direction of the shaft portion 12 from the hub wheel 1 and enables stable torque transmission over a long period of time.

  Since the end of the hub wheel 1 is crimped and preload is applied to the rolling bearing 2, it is not necessary to apply preload by the mouth portion 11 of the outer ring 5. For this reason, it is possible to press-fit the shaft portion 12 of the outer ring 5 without considering the preload to the rolling bearing 2 and to improve the connectivity (assembly property) between the hub wheel 1 and the outer ring 5.

  A sealing material is interposed between the seat surface 60a of the bolt member 54 for fixing the bolt between the hub wheel 1 and the shaft portion 12 of the outer ring 5 and the inner wall 22c, or the end surface 31a of the crimping portion 31 and the mouth portion 11 are By interposing a sealing material between the bottom portion back surface 11a and the like, it is possible to prevent rainwater and foreign matter from entering the concave-convex fitting structure M from the bolt member 54, thereby improving the quality.

  In addition, by arranging the intermediate portion in the protruding direction of the convex portion 35 on the concave portion forming surface before the concave portion is formed, the convex portion 35 bites into the concave portion forming surface during press-fitting, and the concave portion 36 is reliably formed. can do. That is, the press-fitting allowance with respect to the other side of the convex part 35 can be taken sufficiently. As a result, the formability of the concave-convex fitting structure M is stabilized, there is no variation in press-fit load, and a stable torsional strength is obtained.

  In the embodiment shown in FIG. 1 and the like, the convex portion 35 of the concave-convex fitting structure M is provided on the shaft portion 12 of the outer ring 5, and the hardness of the axial end portion of the convex portion 35 is set from the inner diameter portion of the hole of the hub wheel 1. If the shaft portion 12 is press-fitted into the hole portion 22 of the hub wheel 1, the hardness on the shaft portion side can be increased and the rigidity of the shaft portion can be improved.

  By arranging the concave-convex fitting structure M at a position directly below the raceway surface of the rolling bearing 2, occurrence of hoop stress on the bearing raceway surface is suppressed. As a result, it is possible to prevent a bearing failure such as a decrease in rolling fatigue life, occurrence of cracks, and stress corrosion cracking, and a high-quality bearing 2 can be provided.

  As in the above-described embodiment, the spline 41 formed on the shaft portion 12 uses small teeth with a module of 0.5 or less, so that the formability of the spline 41 can be improved and the press-fit load is reduced. Can be achieved. In addition, since the convex part 35 can be comprised with the spline normally formed in this kind of shaft, this convex part 35 can be easily formed at low cost.

  By the way, the outer ring 5 can be pulled out from the hub wheel 1 by removing the bolt member 54 by screwing the bolt member 54 out of the state shown in FIG. That is, the fitting force of the concave-convex fitting structure M can be pulled out by applying a pulling force of a predetermined force or more to the outer ring 5.

For example, the hub wheel 1 and the constant velocity universal joint 3 can be separated by a jig 70 as shown in FIG. The jig 70 includes a base 71, a pressing bolt member 73 that is screwably engaged with the second screw hole 72 of the base 71, and a screw shaft 76 that is screwed into the screw hole 50 of the shaft portion 12. Prepare. A through hole 74 is provided in the base 71, and the bolt 33 of the hub wheel 1 is inserted into the through hole 74, and the nut member 75 is screwed into the bolt 33. At this time, the base 71 and the flange 21 of the hub wheel 1 are overlapped, and the base 71 is attached to the hub wheel 1.

  Thus, after attaching the base 71 to the hub wheel 1 or before attaching the base 71, the screw shaft 76 is screwed into the screw hole 50 of the shaft portion 12 so that the base portion 76a protrudes from the inner wall 22c to the anti-joint side. Combine. The protruding amount of the base portion 76a is set longer than the axial length of the uneven fitting structure M. The screw shaft 76 and the pressing bolt member 73 are disposed on the same axis (on the axis of this wheel bearing device).

Thereafter, the pressing bolt member 73 is screwed into the second screw hole 72 of the base 71 from the opposite joint side, and in this state, is screwed toward the screw shaft 76 side as indicated by an arrow. At this time, since the screw shaft 76 and the pressing bolt member 73 are arranged on the same axis (on the axis of the wheel bearing device), the screw bolt 73 is caused by this screwing. The screw shaft 76 is pressed in the direction of the arrow. As a result, the outer ring 5 moves in the direction of the arrow with respect to the hub ring 1, and the outer ring 5 is detached from the hub ring 1.

  Further, from the state in which the outer ring 5 is detached from the hub wheel 1, the hub wheel 1 and the outer ring 5 can be connected again using, for example, the bolt member 54. That is, with the base 71 removed from the hub wheel 1 and the screw shaft 76 removed from the shaft 12, the projection 35 of the shaft 12 is fitted into the guide recess 44a as shown in FIG. Let Thereby, the phase 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 match. At this time, as shown in FIG. 4A, a radial gap C1 is formed between the top of the projection 35 and the bottom of the guide recess 44a.

In this state, as shown in FIG. 9, the bolt member 54 is screwed into the screw hole 50 of the shaft portion 12 through the bolt insertion hole 56, and the bolt member 54 is screwed into the screw hole 50. Thereby, as shown in FIG. 10B, the shaft portion 12 is fitted into the hub wheel 1. At this time, the hole portion 22 is slightly expanded in diameter, allowing the shaft portion 12 to enter in the axial direction, and intrudes until the bottom back surface 11a of the mouse portion 11 contacts the end surface 31a of the crimping portion 31. . In this case, at the same time, as shown in FIG. 10C, the end surface 35 a of the convex portion 35 comes into contact with the end surface 36 a of the concave portion 36. If the movement in the axial direction is stopped, the hole 22 is reduced in diameter to return to the original diameter. As a result, similar to the previous press-fitting, the concave-convex fitting structure M in which the entire concave portion fitting portion of the convex portion 35 is in close contact with the corresponding concave portion 36 can be reliably reconfigured .

Since the opening of the screw hole 50 of the shaft portion 12 is a tapered portion 50a which widens toward the opening side, there is apt advantage is screwed the screw shaft 76 and the bolt member 54 to the screw hole 50.

  By the way, in the first time (press-fitting for forming the recess 36 in the inner diameter surface 37 of the hole 22), the press-fitting load is relatively large, so it is necessary to use a press machine or the like for press-fitting. On the other hand, in such re-pressing, since the press-fitting load is smaller than the first press-fitting load, the shaft portion 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 outer ring 5 and the hub wheel 1 can be separated and connected in the field.

Moreover, the difference in diameter (diameter gap) between the hole diameter D2 of the bolt insertion hole 56 and the shaft diameter D1 of the non-threaded portion 55a of the bolt member 54 is Δd, and the maximum diameter dimension D3 of the shaft portion 12 in the uneven fitting structure M and the unevenness. When the difference from the minimum diameter dimension D4 of the hole 22 of the hub wheel in the fitting structure M is Δd2, 0 <Δd <Δd2. Therefore, the difference in diameter between the hole diameter D2 of the bolt insertion hole 56 and the shaft diameter D1 of the non-threaded portion 55a of the bolt member 54 is the difference between the maximum diameter dimension D3 of the shaft portion 12 and the minimum diameter dimension D4 of the hub wheel. Smaller than . Thus, since the bolt hole 56 is a shaft press-fitting guide structure unit M3 for guiding the press-fitting direction of the shaft portion when reinject the shaft portion 12 of the outer ring 5, at the time of re-press-fitting the shaft section press-fitting guide structure section M3, The press-fitting of the shaft portion is guided without misalignment. For this reason, stable re-press fitting is possible, and the convex portion 35 is fitted into the concave portion 36 formed previously without being displaced, so that the reassembly can be improved.

  In this way, by applying an axial pulling force to the shaft portion 12 of the outer ring 5, the outer ring 5 can be removed from the hole 22 of the hub wheel 1, so that the workability (maintenance for repair / inspection of each part) is maintained. Property) can be improved. Moreover, by fitting the shaft portion 12 of the outer ring 5 into the hole portion 22 of the hub wheel 1 again after repair and inspection of each part, the fitting contact portion 38 between the convex portion 35 and the concave portion 36 is closely contacted. Structure M can be constructed. For this reason, the wheel bearing device capable of stable torque transmission can be configured again.

  Since the shaft press-fitting guide portion M1 has the guide recess 44a that matches the phase of the projection 35 with the phase of the other recess 36, the shaft portion 12 of the outer hand member is again attached to the hub wheel 1. When press-fitting into the hole 22, it is inserted into the recess 36 formed by the previous press-fitting, and the recess 36 is not damaged. For this reason, the uneven | corrugated fitting structure M which does not produce the clearance gap which produces backlash in a radial direction and the circumferential direction again can be comprised with high precision.

  By forming a gap between the top of the projection 35 and the bottom of the guide recess 44a, etc., the projection 35 can be easily fitted into the guide recess 44a in the pre-press-in process, and the guide recess 44a does not hinder the press-fitting of the convex portion 35. For this reason, the assemblability can be improved.

If the axial length of the bolt insertion hole 56 is too short, a stable guide cannot be exhibited. On the contrary, if the length is too long, the thickness dimension of the inner wall 22c becomes large, and the uneven fitting structure M The axial length cannot be secured, and the weight of the hub wheel 1 is increased. Therefore, various changes can be made in consideration of these.

  In the embodiment, as shown in FIG. 4A, the radial gap C1 is formed between the top of the projection 35 and the bottom of the guide recess 44a, but as shown in FIG. 4B. In addition, circumferential gaps C2 and C2 may be formed between the side portion of the convex portion 35 and the side portion of the guide concave portion 44a. Further, as shown in FIG. 4C, the radial gap C1 between the top of the convex portion 35 and the bottom of the guide concave portion 44a, and the side portion of the convex portion 35 and the side portion of the guide concave portion 44a. A circumferential clearance C2 may be formed between them. By forming such a gap, the protrusion 35 can be easily fitted into the guide recess 44a in the pre-press-in process, and the guide recess 44a does not prevent the protrusion 35 from being press-fitted.

In the spline 41 illustrated in FIG. 2, the pitch of the pitch and valleys 41b at the crest 41a is the same set. For this reason, in the said embodiment, as shown in FIG.2 (b), it respond | corresponds to the circumferential direction thickness L of the protrusion direction intermediate part of the convex part 35, and the said intermediate part between the convex parts 35 adjacent to the circumferential direction. The circumferential dimension L0 at the position is substantially the same.

On the other hand, as shown in FIG. 11A, the circumferential thickness L2 of the projecting direction intermediate portion of the convex portion 35 is set at a position corresponding to the intermediate portion between the convex portions 35 adjacent in the circumferential direction. It may be smaller than the circumferential dimension L1. That is, in the spline 41 formed on the shaft portion 12, the circumferential thickness (tooth thickness) L <b> 2 of the intermediate portion in the protruding direction of the convex portion 35 is set to the peak portion 43 on the hub wheel 1 side fitted between the convex portions 35. It is made smaller than the circumferential thickness (tooth thickness) L1 of the intermediate portion in the protruding direction.

Therefore, the total tooth thickness Σ (B1 + B2 + B3 +...) Of the convex portion 35 on the entire circumference on the shaft 12 side is replaced by the total tooth thickness Σ (A1 + A2 + A3 +...) Of the peak portion 43 (convex tooth) on the hub wheel 1 side.・ It is set smaller than. Thereby, the shear area of the peak 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. When making the sum total of the circumferential thickness of the convex part 35 smaller than the sum total of the circumferential thickness in the peak part 43 of the other party, let the circumferential direction thickness L2 of all the convex parts 35 be the convex parts adjacent to the circumferential direction. It is not necessary to make it smaller than the circumferential dimension L1 between 35. That is, among the plurality of convex portions 35, even if the circumferential thickness of the arbitrary convex portion 35 is the same as the circumferential dimension between the convex portions adjacent in the circumferential direction, it is larger than the circumferential dimension. However, it is sufficient if the sum is small.

  In addition, although the convex part 35 in Fig.11 (a) is made into the trapezoid cross section (Mt. Fuji shape), as a shape of the convex part 35, as shown in FIG.11 (b), an involute tooth shape may be sufficient.

  The shaft press-fitting guide portion M1 may be as shown in FIG. In FIG. 12 (a), the end of the guide recess 44a on the concave-convex fitting structure M side is an inclined surface 77b that is inclined to reduce the diameter along the press-fit direction (press-fit progress direction). That is, the inclination angle θ of the inclined surface 77b is, for example, about 45 °.

  12 (b) and 12 (c), the radial depth dimension of the guide recess 44a is reduced along the press-fitting direction. In FIG. 12B, the end portion on the concave-convex fitting structure M side is a flat surface 77a orthogonal to the press-fitting direction, and in FIG. 12C, the end portion on the concave-convex fitting structure M side is the press-fitting direction (press-fit). The inclined surface 77b is inclined along the traveling direction.

  If the end of the guide recess 44a on the uneven fitting structure side is a flat surface 77a orthogonal to the press-fitting direction, the shaft 12 is received by the flat surface 77a when the shaft 12 is press-fitted into the hole 22. be able to. Moreover, if it is the inclined surface 77b, the convex part 35 can be stably inserted from the recessed part 44a for a guide to the recessed part 36 of the other party. Even if the radial depth of the guide concave portion 44a is reduced along the press-fitting direction, the convex portion 35 can be stably fitted from the guide concave portion 44a to the counterpart concave portion 36.

  Next, FIG. 13 shows a second embodiment. In this case, the hub ring 1 is not provided with the inner wall 22c, and the ring body 80 is mounted in the hole 22 of the hub ring 1 instead of the inner wall 22c. That is, a ring fitting notch 81 is provided in the hole 22 of the hub wheel 1, and the ring body 80 is fitted to the ring fitting notch 81. At this time, the ring body 80 is engaged with the notch end surface 81 a of the ring fitting notch 81. It is preferable that the ring body 80 has a clearance between its outer diameter and the inner diameter of the ring fitting notch 81 as much as possible, or the ring body 80 is press-fitted into the ring fitting notch 81.

  Further, the ring body 80 is formed with a bolt insertion hole 82 through which the bolt member 54 is inserted. The bolt insertion hole 82 has a diameter difference Δd between the hole diameter D2 and the shaft diameter D1 of the non-threaded portion 55a of the bolt member 54 in the same manner as the bolt insertion hole 56 of the first embodiment. When the diameter difference between the shaft outer diameter D3 and the hub wheel inner diameter D4 in the concave-convex fitting structure M is Δd2, 0 <Δd <Δd2.

  The other configuration of the wheel bearing device shown in FIG. 13 is the same as that of the wheel bearing device shown in FIG. 1, and therefore, the same members as those in FIG. .

  For this reason, even if it is a wheel bearing apparatus shown in FIG. 13, there exists an effect similar to the wheel bearing apparatus shown in FIG. Moreover, since the bolt insertion hole 82 is formed in the ring body 80 which is a separate member from the hub wheel 1, the bolt insertion hole 82 can be stably formed with high accuracy. Further, even when the ring body 80 is damaged or the like, it can be replaced, and it is not necessary to replace the entire hub wheel 1, so that the cost can be reduced.

By the way, in each said embodiment, while forming the spline 41 which comprises the convex part 35 in the axial part 12 side, the hardening process is performed with respect to the spline 41 of this axial part 12, and the internal diameter surface of the hub ring 1 is unhardened. (Raw material). On the other hand, as shown in FIG. 14 as a reference example, a spline 61 (consisting of a crest 61a and a trough 61b) is formed on the inner diameter surface of the hole 22 of the hub wheel 1 and cured. The shaft portion 12 may not be subjected to a curing process. The spline 61 can also be formed by various processing methods such as broaching, cutting, pressing, and drawing, which are publicly known means. Further, various heat treatments such as induction hardening and carburizing and quenching can be employed as the thermosetting treatment.

In this case, the intermediate portion in the protruding direction of the convex portion 35 corresponds to the position of the concave portion forming surface (the outer diameter surface of the shaft portion 12) before the concave portion is formed. That is, the diameter dimension (minimum diameter dimension of the convex portion 35) D8 of the circle connecting the vertices of the convex portion 35 which is the peak portion 61a of the spline 61 is smaller than the outer diameter size D6 of the shaft portion 12, and the valley portion of the spline 61 The diameter dimension ( maximum diameter dimension between convex parts) D9 of the circle connecting the bottoms of 61b is set to be larger than the outer diameter dimension D10 of the shaft part 12. That is, D8 <D10 <D9.

  If the shaft portion 12 is press-fitted into the hole portion 22 of the hub wheel 1, the concave portion 36 into which the convex portion 35 is fitted can be formed on the outer peripheral surface of the shaft portion 12 by the convex portion 35 on the hub wheel 1 side. Thereby, the whole fitting contact part 38 of the convex part 35 and the recessed part fitted to this is closely_contact | adhered.

  Here, the fitting contact portion 38 is a range B shown in FIG. 14B, and is a range from the middle of the mountain shape to the top of the mountain in the cross section of the convex portion 35. Further, a gap 62 is formed on the outer diameter side of the outer peripheral surface of the shaft portion 12 between the adjacent convex portions 35 in the circumferential direction.

  Even in the case shown in FIG. 14, it is preferable to provide the shaft press-fitting guide portion M1. In this case, a guide recess 44b may be provided on the shaft portion 12 side. Further, a radial gap C1 is formed between the top of the convex portion 35 and the bottom of the guide concave portion 44a, or a circumferential gap C2 between the side portion of the convex portion 35 and the side portion of the guide concave portion 44a, C2 can be formed, and further, the radial gap C1 and the circumferential gaps C2 and C2 can be formed.

  Even in the case shown in FIG. 14, since the protruding portion 45 is formed by press-fitting, it is preferable to provide a storage portion 57 for storing the protruding portion 45. Since the protruding portion 45 is formed on the mouse side of the shaft portion 12, the storage portion is provided on the hub wheel 1 side.

  As described above, the convex portion 35 of the concave-convex fitting structure M is provided on the inner diameter surface 37 of the hole portion 22 of the hub wheel 1, and the hardness of the axial end portion of the convex portion 35 is set to the outer diameter of the shaft portion 12 of the outer ring 5. In the case of press-fitting higher than the portion, it is not necessary to perform the hardness treatment (heat treatment) on the shaft portion side, so that the productivity of the outer joint member (outer ring 5) of the constant velocity universal joint is excellent.

As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications are possible. For example, as the shape of the convex portion 35 of the concave-convex fitting structure M, FIG. In the embodiment shown in FIG. 2, the cross section is triangular, and in the embodiment shown in FIG. 11A, the cross section is trapezoidal (mountain shape), but other shapes such as a semicircular shape, a semielliptical shape, and a rectangular shape are available. The area of the convex part 35, the number, the circumferential arrangement pitch, and the like can be arbitrarily changed. That is, it is not necessary to form the spline 41 and use the crest portion (convex tooth) 41a of the spline 41 as the convex portion 35 of the concave-convex fitting structure M, and it may be a key or a curved wave. It may form a mating surface of the mold. In short, the convex portion 35 disposed along the axial direction can be press-fitted into the mating side, and the concave portion 36 can be formed on the mating side with the convex portion 35 so as to closely fit the convex portion 35. It is only necessary that the entire fitting contact portion 38 between the portion 35 and the concave portion fitted thereto is in close contact, and that rotational torque can be transmitted between the hub wheel 1 and the constant velocity universal joint 3.

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 of the shaft portion 12 fitted into the hole 22 is also a polygon other than a circular cross section. It may be an irregular cross section. Furthermore, since only the press-fitting start end portion of the convex portion 35 needs to be harder than the portion where the concave portion 36 is formed when the shaft portion 12 is press-fitted into the hub wheel 1, it is necessary to increase the overall hardness of the convex portion 35. There is no. In FIG. 3 and the like, the gap 40 is formed, but the inner diameter surface 37 of the hub wheel 1 may bite into the valley between the convex portions 35. Note that the hardness difference between the convex portion 35 side and the concave portion forming surface side formed by the convex portion 35 is preferably 20 points or more in HRC, but 20 points if the convex portion 35 can be press-fitted. It may be less.

  Although the end surface (press-fit start end) of the convex portion 35 is a surface orthogonal to the axial direction in the embodiment, it may be inclined at a predetermined angle with respect to the axial direction. In this case, it may be inclined from the inner diameter side toward the outer diameter side toward the anti-convex portion side or inclined toward the convex portion side.

  Furthermore, you may provide the small recessed part arrange | positioned by the predetermined pitch along the circumferential direction in the internal diameter surface 37 of the hole 22 of the hub wheel 1. FIG. The small recess needs to be smaller than the volume of the recess 36. By providing such a small recess, the press-fit property of the protrusion 35 can be improved. That is, by providing the small concave portion, the capacity of the protruding portion 45 formed when the convex portion 35 is press-fitted can be reduced, and the press-fit resistance can be reduced. Moreover, since the protrusion part 45 can be decreased, the volume of the storage part 57 can be reduced, and the workability of the storage part 57 and the strength of the shaft part 12 can be improved. Various shapes such as a semi-elliptical shape and a rectangular shape can be adopted as the shape of the small concave portion, and the number can be arbitrarily set.

  A roller may be used as the rolling element 30 of the bearing 2. In the above-described embodiment, the third generation wheel bearing device is shown. However, the first generation, the second generation, or the fourth generation may be used. 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 the side where the recess 36 is formed may be moved or both may be moved. In the constant velocity universal joint 3, the inner ring 6 and the shaft 10 may be integrated via the concave / convex fitting structure M described in the above embodiments.

  The sealing material interposed between the seat surface 60a of the bolt member 54 that fixes the hub wheel 1 and the shaft portion 12 with the bolt and the inner wall 22c is made of resin on the seat surface 60a side of the bolt member 54 in the embodiment. However, conversely, a resin may be applied to the inner wall 22c side. Moreover, you may make it apply | coat resin to the seat surface 60a side and the inner wall 22c side. When the bolt member 54 is screwed, such a sealing material is omitted if the seat surface 60a of the bolt member 54 and the bottom surface of the recessed portion 51 of the inner wall 22c are excellent in adhesion. Is also possible. That is, it is possible to improve the adhesiveness of the bolt member 54 with the seating surface 60a by grinding the bottom surface of the recessed portion 51. Of course, the sealing material can be omitted if the adhesiveness can be exhibited even in a so-called turning finished state without grinding the bottom surface of the recessed portion 51.

  As shown in FIGS. 4A, 4B, and 4C, the guide recesses 44a are formed with gaps C1 and C2 between the protrusions 35. It is only necessary that the misalignment or the tilt of the core does not occur at the time of press-fitting, and the convex part 35 presses against the inner surface of the guide concave part 44a so as not to increase the press-fitting load. Further, the axial length of the guide recess 44a can be arbitrarily set, and if it is long, it is preferable for alignment, but the upper limit is limited by the axial length of the hole 22 of the hub wheel 1. On the contrary, if the axial length of the hole 22 of the hub wheel 1 is short, the hub wheel 1 may not function as a guide and may cause misalignment or tilt. For this reason, it is necessary to determine the axial length of the guide recess 44a in consideration of these.

  Moreover, the cross-sectional shape of the guide recess 44a is not limited to that shown in FIG. Various changes can be made according to the cross-sectional shape and the like of the convex portion 35. The number of guide recesses 44a may be smaller or larger than the number of projections 35 without matching the number of projections 35. In short, it is only necessary that some convex portions 35 are fitted in some guide concave portions 44a so that the phase of the convex portions 35 coincides with the phase of the concave portion 36 formed by the previous press-fitting.

  The inclination angle θ of the inclined surface 77b at the end of the guide recess 44a and the inclination angle θ1 of the bottom of the guide recess 44a can be arbitrarily changed. If the inclination angle θ of the inclined surface 77b is close to 90 °, it is functionally the same as the flat surface 77a orthogonal to the press-fitting direction. If the inclination angle θ is small, the guide recess 44a becomes longer, and the concave-convex fitting structure M The axial length of is shortened. Moreover, if the inclination | tilt angle (theta) 1 of a bottom part becomes large, the structure of the recessed part 44a for guides will become difficult, and if it is small conversely, the function in the case of making it incline cannot be exhibited. For this reason, it is necessary to set the inclination angles θ and θ1 in consideration of these.

  Although the outer member 25 of the rolling bearing 2 in the above embodiment does not have a vehicle body mounting flange, the outer member 25 may have a vehicle body mounting flange.

It is a longitudinal cross-sectional view of the wheel bearing apparatus which shows 1st Embodiment of this invention. It is an expanded longitudinal cross-sectional view of the said uneven | corrugated fitting structure. The uneven | corrugated fitting structure of the said wheel bearing apparatus is shown, (a) is the ZZ sectional view taken on the line of FIG. 2, (b) is the X section enlarged view of (a). The shaft part press-fit guide part of the said wheel bearing apparatus is shown, (a) is the WW sectional view of FIG. 2, (b) is an expanded sectional view which shows the 1st modification of a shaft part press-fit guide part . (C) is an expanded sectional view which shows the 2nd modification of a shaft part press-fit guide part . It is a principal part enlarged view of the said wheel bearing apparatus. It is sectional drawing which shows the decomposition | disassembly state of the said wheel bearing apparatus. It is sectional drawing which shows the isolation | separation method of an uneven | corrugated fitting structure. It is sectional drawing which shows the repressing method. It is sectional drawing which shows the repressing method. The re-pressing method is shown, (a) is a cross-sectional view showing a state immediately before press-fitting, (b) is a cross-sectional view showing the press-fitting process, and (c) is a cross-sectional view showing a press-fitting completion state. It is sectional drawing which shows the modification of an uneven | corrugated fitting structure. The shaft part press fit guide structure is shown, (a) is a sectional view of the first modification, (b) is a sectional view of the second modification, and (c) is a sectional view of the third modification. It is a longitudinal cross-sectional view of the wheel bearing apparatus which shows 2nd Embodiment of this invention. The wheel bearing apparatus which shows 3rd Embodiment of this invention is shown, (a) is a cross-sectional view. (B) is the Y section enlarged view of (a). It is sectional drawing of the conventional wheel bearing apparatus.

DESCRIPTION OF SYMBOLS 1 Hub wheel 2 Bearing 3 Constant velocity universal joint 11 Mouse | mouth part 22 Hole part 22c Inner wall 24 Inner ring 31 Clamping part 35 Convex part 36 Concave part 38 Contact part 54 Bolt member 55a Non-thread part 56 Bolt insertion hole 60a Seat surface
71 base
72 second screw hole M recess-projection fitting structure M3 shaft section press-fitting guide structure section M5 bolt coupling means

Claims (6)

A hub wheel having a flange for mounting on the wheel; an outer raceway surface disposed on an outer peripheral side of the hub wheel; an inner raceway surface facing the outer raceway surface; and an outer raceway surface and an inner raceway surface facing each other. The shaft of the outer joint member of the constant velocity universal joint that is united with the double row rolling bearing having the rolling elements disposed between and the constant velocity universal joint having the outer joint member and is fitted into the hole of the hub wheel A wheel bearing device in which the part is detachably coupled to the hub wheel,
Serrations having a plurality of convex portions extending in the axial direction provided on the outer diameter surface of the shaft portion of the outer joint member are arranged on the small concave portions provided on the inner diameter surface of the hole portion of the hub wheel at a predetermined pitch. Correspondingly, it press-fits along the axial direction into the hole inner diameter surface of the hub wheel, and forms a recess in the hole inner diameter surface of the hub wheel by cutting with the press-fitted protrusion, and the protrusion and the recess fit together. Consists of a concave-convex fitting structure where the entire contact area adheres,
A bolt insertion hole is provided integrally with or separately from the hub wheel, a screw hole into which the bolt member is screwed is provided on the shaft center of the shaft portion, and the bolt member is screwed into the screw hole via the bolt insertion hole. In this way, the hub wheel and the shaft portion of the outer joint member are fixed, and by removing the bolt member from the screw hole, separation of the hub wheel and the shaft portion of the outer joint member is allowed,
A female serration that can be fitted to each convex portion through one or both of a radial clearance and a circumferential clearance on the end of the hub ring hole inner diameter surface that is the press-fitting start side of the convex portion. A shaft-shaped press-fit guide part is provided,
A wheel bearing device , wherein a bolt member inserted into a bolt insertion hole can be screwed into a screw hole in a state in which a convex portion is fitted to a shaft portion press-fitting guide portion . The bolt member has a threaded portion and a non-threaded portion, and there is a diameter gap between the bolt insertion hole and the non-threaded portion of the bolt member inserted through the bolt insertion hole. The wheel bearing device according to claim 1, wherein a difference between a maximum diameter dimension of a shaft portion of the outer joint member and a minimum diameter dimension of a hole portion of the hub wheel in the uneven fitting structure is smaller. The wheel bearing device according to claim 1 or 2, wherein an inner wall for partitioning the inside of the hub wheel is provided in the hole portion, and the bolt insertion hole is provided in the inner wall. The wheel bearing device according to any one of claims 1 to 3, wherein a spline module of the shaft portion is 0.5 or less. The bolt member of the wheel bearing device according to any one of claims 1 to 4 is removed from the screw hole to separate the hub wheel and the shaft portion of the outer joint member, and then the serration of the shaft portion is removed from the shaft portion. The shaft of the outer joint member is fitted into the press-fitting guide, screwed into the screw hole through the bolt insertion hole, and screwed into the screw hole while guiding the bolt member with the bolt insertion hole. A bearing for a wheel, characterized in that a concave-convex fitting structure is formed in which a portion is fitted into a hole of a hub wheel and a convex portion is press-fitted into a concave portion so that the entire fitting contact portion of the convex portion and the concave portion is in close contact with each other. Device reassembly method. A method for separating the wheel bearing device according to any one of claims 1 to 4 ,
The screw shaft is screwed into the screw hole of the shaft portion, the base having the second screw hole is attached to the hub wheel, and the bolt member screwed into the second screw hole of the base is screwed to the screw shaft in the axial direction. A separation method for a wheel bearing device, wherein the hub wheel and the shaft portion of the outer joint member are separated by applying a pressing force.

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