Wheel bearing device

Abstract

To provide a wheel bearing device that facilitates assembly of a face spline without deteriorating the sealing performance of a seal member that prevents muddy water from entering the face spline.SOLUTION: A wheel bearing device comprises: an outer ring 2; an inner member including a hub ring 3 and an inner ring 4; balls 7; a constant velocity universal joint 20 coupled to the hub ring 3; and an inner-side seal member 9 which seals between the outer ring 2 and the inner ring 4. A face spline 11a and a face spline 25a are formed on an inner-side end face of the hub ring 3, and a shoulder portion 25 of the constant velocity universal joint 20. A cover member 17 is provided to protect an outer diameter side of the face spline 11a and the face spline 25a. An inner diameter of the cover member 17 is formed so as to increase in diameter toward the inner side.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a technology for a wheel bearing device. [Background technology]

[0002] Conventionally, double-row angular contact ball bearings have been commonly used as bearing assemblies for automobile wheels, and include an outer member, an inner member, and balls held in raceways formed on the outer member and the inner member, respectively.

[0003] A flange is formed at one end of the inner member, and a tire wheel, brake disc, etc. (not shown) are attached to the flange. A fixing flange is formed on the outer peripheral surface of the outer member for attachment to a vehicle body member (not shown) supported by the vehicle suspension system.

[0004] The rotational driving force of the drive shaft is transmitted to the inner member via a constant velocity universal joint. One known method for transmitting the rotational driving force is to form a spline tooth portion (face spline) on a crimped portion that secures the inner member, and to engage this spline tooth portion with teeth (face spline) formed on an end face of an outer ring of the constant velocity joint (see, for example, Patent Document 1).

[0005] In addition, a slinger is provided on the outer diameter of the crimped portion, and the slinger comprises a cylindrical portion that is press-fitted into the inner member and a standing portion that extends radially outward from the cylindrical portion. A known method for controlling the press-fitting of the cylindrical portion of the slinger is to press-fit the slinger while aligning the inner ring end face with the slinger by abutting a step in the core metal of the slinger against the inner ring end face. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] German Patent Application Publication No. 102006032159 Summary of the Invention [Problem to be solved by the invention]

[0007] However, in conventional wheel bearing devices, it is difficult to position the face spline when assembling it, and poor positioning can sometimes prevent the bolts that secure the constant velocity universal joint from being properly tightened. Also, when assembling the face spline, if a sealant is provided to prevent muddy water from entering the face spline of the outer ring of the wheel bearing device and the constant velocity universal joint, the sealant can be damaged by coming into contact with the teeth of the face spline of the constant velocity universal joint, which can reduce muddy water resistance.

[0008] The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a wheel bearing device that can facilitate the assembly of a face spline without reducing the sealing performance of a seal member that prevents muddy water from entering the face spline. [Means for solving the problem]

[0009] That is, an outer member having an outer raceway surface on its inner periphery; an inner member having an inner raceway surface facing the outer raceway surface; a rolling element accommodated between the outer raceway surface and the inner raceway surface so as to be able to roll freely; a constant velocity universal joint connected to the inner member; a seal member that seals between the outer member and the inner member; A wheel bearing device comprising: a face spline is formed on an inner side end surface of the inner member and on a shoulder portion of the constant velocity universal joint, a cover member for protecting an outer diameter side of the face spline; The inner diameter of the cover member is formed to increase toward the inner side. It is something. [Effects of the Invention]

[0010] The present invention has the following effects. That is, the wheel bearing device of the present invention protects the crimped portion and the fitting portion of the face spline formed in the constant velocity universal joint, while improving workability and maintainability during assembly of the wheel bearing device. [Brief explanation of the drawings]

[0011] [Figure 1] 1 is a partial cross-sectional view showing a wheel bearing device according to a first embodiment of the present invention; [Figure 2] 1 is a partial cross-sectional view showing an inner side portion of a wheel support bearing device according to a first embodiment of the present invention; [Figure 3] FIG. 2 is a partially enlarged cross-sectional view showing a cover member and a face spline according to the first embodiment of the present invention. [Figure 4] FIG. 10 is a partially enlarged cross-sectional view showing a cover member and a face spline according to a second embodiment of the present invention. [Figure 5] FIG. 10 is a partially enlarged cross-sectional view showing a cover member and a face spline according to a third embodiment of the present invention. [Figure 6] FIG. 10 is a partially enlarged cross-sectional view showing a cover member and a face spline according to a fourth embodiment of the present invention. [Figure 7] FIG. 11 is a partially enlarged cross-sectional view showing a cover member and a jig for attaching the cover member according to a fifth embodiment of the present invention. [Figure 8] FIG. 10 is a partially enlarged cross-sectional view showing a cover member and a jig for attaching the cover member according to a sixth embodiment of the present invention. [Figure 9] FIG. 10 is a partially enlarged cross-sectional view showing a cover member and a face spline according to a sixth embodiment of the present invention. [Figure 10] FIG. 10 is a partial cross-sectional view showing a wheel bearing device according to a seventh embodiment of the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0012] (First embodiment) Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[0013] A wheel bearing device 1 shown in FIG. 1 is one embodiment of a wheel bearing device according to the present invention, and supports a wheel rotatably in a suspension system of a vehicle such as an automobile.

[0014] As shown in Figure 1, the wheel bearing device 1 has a configuration known as a third generation, and includes an outer ring 2 as an outer member, a hub ring 3 and an inner ring 4 as inner members, two rolling rows of inner ball rows 5 and outer ball rows 6, an inner sealing member 9, an outer sealing member 10, and a constant velocity universal joint 20.

[0015] Here, the inner side refers to the vehicle body side of the wheel bearing device 1 when it is attached to the vehicle body, and the outer side refers to the wheel side of the wheel bearing device 1 when it is attached to the vehicle body. The axial direction refers to the direction along the rotation axis X of the wheel bearing device 1, with one axial end side being the outer side and the other axial end side being the inner side. The direction perpendicular to the rotation axis of the wheel bearing device 1 is referred to as the radial direction. In the following description, the term "cross section" will be used to refer to a cross section that passes through the rotation axis of the wheel bearing device 1 and is parallel to the rotation axis of the wheel bearing device 1.

[0016] 1, an inner-side outer raceway groove 2c and an outer-side outer raceway groove 2d are formed on the inner peripheral surface of the outer ring 2. A vehicle body mounting flange 2e for mounting the outer ring 2 to a vehicle body member is integrally formed on the outer peripheral surface of the outer ring 2.

[0017] The inner end of the outer peripheral surface of the hub wheel 3 is formed with a small-diameter step 3a that is smaller in diameter than the outer end. A wheel mounting flange 3b for mounting a wheel is formed integrally with the outer end of the hub wheel 3. A plurality of bolt holes 3d are formed in the wheel mounting flange 3b. Hub bolts (not shown) for fastening the hub wheel 3 to a wheel or brake component are press-fitted into the bolt holes 3d. The wheel mounting flange 3b is an example of a hub flange that extends radially outward.

[0018] An outer-side inner raceway groove 3c is provided on the outer peripheral surface of the hub wheel 3 so as to face the outer-side outer raceway groove 2d of the outer ring 2. In other words, the inner raceway groove 3c is defined by the hub wheel 3 on the outer side of the inner member. An outer-side opening 2b, which is an annular space, is formed between the outer ring 2 and the hub wheel 3. An outer-side seal member 10 is fitted into the outer-side opening 2b and closes it. The outer-side seal member 10 is an example of a sealing device. A shaft hole 3f is provided inside the hub wheel 3. The shaft hole 3f is formed along the axial direction, and a constant velocity universal joint 20 is coupled to the inner-side end face. The outer-side end face opens to the bottom surface of the recess 3g.

[0019] The inner ring 4 is mounted on the small diameter step 3a of the hub wheel 3. The inner ring 4 is press-fitted into the small diameter step 3a with a predetermined interference. Furthermore, the hub wheel 3 and the inner ring 4 are integrated by a crimped portion 11, which is plastically deformed by crimping the inner end of the small diameter step 3a of the hub wheel 3, and prevents the inner ring 4 from slipping out of the hub wheel 3 in the axial direction. At the inner end where the crimped portion 11 is provided, the shaft hole 3f is formed to have an expanded diameter.

[0020] The crimped portion 11 has a face spline 11a. The face spline 11a is formed on the inner end surface of the crimped portion 11. The face spline 11a has a plurality of protruding portions protruding from the inner end surface of the crimped portion 11 and a plurality of recessed portions provided between the protruding portions. The protruding portions and recessed portions each extend in the radial direction and are arranged alternately in the circumferential direction.

[0021] The inner ring 4 applies preload to the inner ball row 5 and outer ball row 6, which are rolling rows. An inner-side inner raceway groove 4a is provided on the outer peripheral surface of the inner ring 4 so as to face the inner-side outer raceway groove 2c of the outer ring 2. In other words, the inner ring 4 defines the inner raceway groove 4a on the inner side of the inner member. An inner-side opening 2a, which is an annular space, is formed between the outer ring 2 and the inner ring 4. An inner-side seal member 9 is fitted into the inner-side opening 2a and closes it. The inner-side seal member 9 is an example of a sealing device.

[0022] The inner side seal member 9 is a sealing mechanism that seals (blocks) the inner side opening 2a between the outer ring 2 and the hub wheel 3, and is composed of, for example, a two-side lip type pack seal in which two seal lips are in contact or close to each other.

[0023] The inner ball row 5 and outer ball row 6, which are rolling rows, are formed by a plurality of balls 7, which are rolling elements, held in a cage. The inner ball row 5 is rollably sandwiched between the inner raceway groove 4a of the inner ring 4 and the inner-side outer raceway groove 2c of the outer ring 2. The outer ball row 6 is rollably sandwiched between the inner raceway groove 3c of the hub ring 3 and the outer-side outer raceway groove 2d of the outer ring 2. In other words, the inner ball row 5 and the outer ball row 6 are rollably housed between the raceway grooves of the outer member and the inner member. In the wheel bearing device 1, the outer ring 2, the hub ring 3, the inner ring 4, the inner ball row 5, and the outer ball row 6 form a double-row angular contact ball bearing. Note that the wheel bearing device 1 may be formed by a double-row tapered roller bearing.

[0024] The constant velocity universal joint 20 is provided at one end of an intermediate shaft (not shown) that constitutes the drive shaft, and is connected to the hub wheel 3. The constant velocity universal joint 20 is a joint that freely changes the angle at which the drive shaft and the wheel bearing device join, and is a member that absorbs misalignment in angle and position between the intermediate shaft and the hub wheel hole of the wheel bearing device 1.

[0025] The constant velocity universal joint 20 comprises a bowl-shaped mouth portion 24 configured to taper in diameter toward the outer side, a shoulder portion 25 that forms the bottom of the mouth portion 24 at the outer side portion of the mouth portion 24, and an assembly bolt hole 26 provided on the inner diameter side of the shoulder portion 25 for inserting an assembly bolt 27.

[0026] The shoulder portion 25 is provided with a face spline 25a that engages with the face spline 11a of the crimped portion 11 of the hub wheel 3. The face spline 25a is formed on the end surface of the shoulder portion 25 on the outer side.

[0027] The face spline 25a has a plurality of protruding portions protruding from the shoulder portion 25 toward the outer side and a plurality of recessed portions provided between the protruding portions. The protruding portions and recessed portions each extend in the radial direction and are arranged alternately in the circumferential direction.

[0028] 1 and 2, the assembly bolt hole 26 is a hole provided in the radial center of the shoulder portion 25, and has a female thread formed on its inner peripheral surface. A support cylinder portion 26a is formed on the outer wall portion on the outer side of the assembly bolt hole 26. The support cylinder portion 26a protrudes further outward than the outer end face of the shoulder portion 25. A groove 26b is formed on the outer periphery of the support cylinder portion 26a.

[0029] An assembly bolt hole 26 formed on the inner diameter side of the shoulder portion 25 is aligned so that its central axis coincides with that of the axial hole 3f inside the hub wheel 3. By inserting an assembly bolt 27 from the outer side of the axial hole 3f and screwing it into the assembly bolt hole 26, the face spline 11a of the crimped portion 11 of the hub wheel 3 and the face spline 25a of the shoulder portion 25 of the outer joint member 21 are held in an engaged state, and torque from the drive shaft can be transmitted to the hub wheel 3 via the outer joint member 21.

[0030] That is, the concave and convex portions of the face spline 11a and the concave and convex portions of the face spline 25a are supported in a meshed state, thereby enabling torque from the drive shaft to be transmitted to the hub wheel 3 via the constant velocity universal joint 20. By employing such a face spline structure, torque can be transmitted without backlash, and the generation of stick-slip noise between the hub wheel 3 and the mouth portion 24 can be suppressed. Furthermore, compared to a shaft spline structure, there is no need to provide a stem portion in the axial direction, which allows for a shorter installation area, thereby enabling a smaller size and lighter weight. More specifically, the axial length of the constant velocity universal joint 20 can be shortened.

[0031] [Cover material] Next, the cover member 17 for covering the fitting portion of the face spline 11a and the face spline 25a will be described with reference to FIGS.

[0032] The cover member 17 is formed in a cylindrical shape, and the outer end of the cover member 17 is sandwiched between the fitting surface of the inner seal member 9 with the inner ring 4 and the outer diameter surface of the inner ring 4. The cover member 17 and the inner seal member 9 may be integral or separate. The cover member 17 has a contact portion 17a that extends radially inward so as to fit along the inner end face of the inner ring 4, and a cover tube portion 17b that is bent and extends toward the inner side at the inner diameter end of the contact portion 17a.

[0033] By bringing the contact portion 17a into contact with the inner side end surface of the inner ring 4, the positioning of the cover member 17 with respect to the inner ring 4 can be easily performed.

[0034] As shown in Fig. 3, the cover member 17 is curved in cross section so that its diameter increases from the cover tubular portion 17b toward the inner side. That is, the entrance side when the constant velocity universal joint is fitted is formed in a tapered shape. "The cover member 17 increases in diameter toward the inner side" means that the diameter of the inner end of the cover tubular portion 17b is larger than the diameter of the outer end. In other embodiments (Figs. 4 to 10), the diameter of the inner end of the cover tubular portion 17b is also larger than the diameter of the outer end, and therefore this is also included in the description of the cover member 17 increasing in diameter toward the inner side.

[0035] The inner diameter d1 of the non-expanded portion of the cover tubular portion 17b is formed to be larger than the outer diameter d2 of the shoulder portion 25 of the constant velocity universal joint 20. This reduces the possibility that the shoulder portion 25 of the constant velocity universal joint 20 and the cover tubular portion 17b will come into contact with each other, hindering assembly.

[0036] The ratio of the inner diameter d1 of the non-expanded portion of the cover tubular portion 17b to the outer diameter d2 of the shoulder portion 25 of the constant velocity universal joint 20 is greater than 100% and less than or equal to 103%. This configuration reduces the possibility that the shoulder portion 25 of the constant velocity universal joint 20 and the cover tubular portion 17b will come into contact and hinder assembly, thereby improving assembly efficiency. In addition, the gap between the inner diameter of the cover tubular portion 17b and the outer diameter of the shoulder portion 25 of the constant velocity universal joint 20 is reduced, preventing dust from easily entering.

[0037] Furthermore, during assembly, the cover tubular portion 17b and the constant velocity universal joint 20 can be prevented from being significantly misaligned in their central positions. For example, as shown in FIG. 2, when the shoulder portion 25 of the constant velocity universal joint 20 is moved axially outward and into the shaft hole of the hub wheel 3, the outer peripheral surface of the shoulder portion 25 of the constant velocity universal joint 20 is guided by the inner peripheral surface of the cover tubular portion 17b of the cover member 17. This allows the cover tubular portion 17b and the constant velocity universal joint 20 to be assembled with their central positions aligned. This improves the radial positioning accuracy of the fitting portions of the face spline 11a and the face spline 25a, and prevents the assembly bolts 27 from loosening.

[0038] Furthermore, when assembling the constant velocity universal joint 20, the shoulder 25 of the constant velocity universal joint 20 abuts against the cover tubular portion 17b, thereby achieving a temporary fastening function, without the assembly bolt 27 being inserted. If the gap between the inner diameter of the cover tubular portion 17b and the outer diameter of the shoulder 25 of the constant velocity universal joint 20 becomes too large, the retention function decreases, so it is preferable that the gap be 103% or less.

[0039] A face spline seal member 18 is provided at the inner end of the cover cylindrical portion 17b. The face spline seal member 18 comes into sliding contact with the outer peripheral surface of the shoulder portion 25 of the constant velocity universal joint 20, thereby preventing dust from entering the mating portion between the face spline 11a and the face spline 25a from the outside. The face spline seal member 18 is made of synthetic rubber such as NBR or FKM.

[0040] The face spline seal member 18 covers the inner end surface of the cover tubular portion 17b and is joined to a portion of the outer diameter surface and a portion of the inner diameter surface. The face spline seal member 18 joined to a portion of the inner diameter surface forms the abutment surface with the shoulder portion 25 of the constant velocity universal joint 20. By vulcanizing the face spline seal member 18 only on the inner end portion of the cover tubular portion 17b in this manner, the face spline seal member 18 is prevented from being damaged by abutment with the face spline 25a during assembly, and a decrease in muddy water resistance is prevented. Furthermore, maintaining the muddy water resistance makes it easier to prevent external dust from entering the mating portion between the face spline 11a and the face spline 25a, improving maintainability.

[0041] In addition, the expansion angle of the expanded diameter portion of the cover cylindrical portion 17b is formed to be approximately the same as the expansion angle of the constant velocity universal joint 20. This makes it easier to position the face spline seal member 18 of the cover cylindrical portion 17b and the shoulder portion 25 of the constant velocity universal joint 20 at the location where they make sliding contact.

[0042] As described above, the wheel bearing device according to the present invention comprises the outer ring 2, which is an outer member having outer raceway grooves 2c and 2d on its inner circumference, the inner member made up of the hub ring 3 and inner ring 4, which have inner raceway grooves 3c and 4a facing the outer raceway grooves 2c and 2d, balls 7, which are rolling elements housed for free rolling between the outer raceway grooves 2c and 2d and the inner raceway grooves 3c and 4a, a constant velocity universal joint 20 connected to the hub ring 3, and an inner seal member 9, which seals between the outer ring 2 and the inner ring 4. A crimped portion 11 is provided at the inner end of the hub ring 3, and face splines 11a and 25a are formed on the inner end surface of the crimped portion 11 and on the shoulder 25 of the constant velocity universal joint 20. A cover member 17 is provided to protect the outer diameter sides of the face splines 11a and 25a, and the inner diameter of the cover member 17 is formed so as to increase in diameter toward the inner side. With this configuration, the possibility of the shoulder portion 25 of the constant velocity universal joint 20 and the cover tubular portion 17b coming into contact with each other and hindering assembly is reduced.

[0043] Furthermore, the inner diameter d1 of the inner end portion of the cover member 17 is greater than 100% and less than 103% of the outer diameter d2 of the constant velocity universal joint 20. This configuration increases the gap between the inner diameter of the cover tubular portion 17b and the outer diameter of the shoulder portion 25 of the constant velocity universal joint 20, preventing dust from easily getting in. Furthermore, during assembly, the cover tubular portion 17b and the constant velocity universal joint 20 can be assembled while preventing significant deviation in their central positions.

[0044] (Second embodiment) As a second embodiment, as shown in FIG. 4, the face spline seal member 18 may have a first lip 18a and a second lip 18b. The first lip 18a is a lip that extends at an angle radially outward from the inner end of the face spline seal member 18. The second lip 18b is a lip that extends from the outer side of the first lip 18a. The first lip 18a and the second lip 18b come into sliding contact with the outer peripheral surface of the shoulder portion 25 of the constant velocity universal joint 20, thereby preventing external dust from entering the mating portion between the face spline 11a and the face spline 25a.

[0045] With this configuration, compared to when the face spline seal member 18 is in sliding contact directly with the outer peripheral surface of the shoulder portion 25, the sliding contact occurs only at the tips of the first lip 18a and the second lip 18b, thereby reducing frictional resistance and preventing the inflow of dust from outside.

[0046] (Third embodiment) As a third embodiment, as shown in FIG. 5, a recess 28 may be provided on the outer diameter of constant velocity universal joint 20, and an engaging protrusion 17c that engages with recess 28 may be provided on the inner diameter of cover member 17. The recess 28 is provided by cutting on the outer diameter surface of the shoulder portion 25 of the constant velocity universal joint 20. The recess 28 is formed with inclined side surfaces on the inner side and outer side.

[0047] The engaging projection 17c of the cover member 17 is formed by raising a portion of the cylindrical cover tubular portion 17b toward the inner diameter side. When the concave and convex portions of the face spline 11a provided on the crimped portion 11 engage with the face spline 25a provided on the shoulder portion 25 of the constant velocity universal joint 20, the constant velocity universal joint 20 is assembled to the hub wheel 3 along the inner diameter of the cover tubular portion 17b, guided by the cover member 17.

[0048] With this configuration, the engaging projection 17c of the cover member 17 can be temporarily fixed by engaging with the recess 28 provided in the shoulder portion 25 of the constant velocity universal joint 20, preventing the constant velocity universal joint 20 from being inserted excessively toward the outer side and allowing it to be assembled in an appropriate position. Note that the engaging projection 17c of the cover tubular portion 17 abuts against the outer diameter of the shoulder portion 25 during assembly, which reduces assembly ease, but improves positioning effectiveness through temporary fixing. Furthermore, the assembled state can be easily determined by whether or not the engaging projection 17c and the recess 28 are engaged, thereby improving assembly ease.

[0049] (Fourth embodiment) As a fourth embodiment, as shown in Figure 6, the constant velocity universal joint 20 may be configured to have a stem portion 36 that is inserted into the axial hole 3f inside the hub wheel 3. The stem portion 36 is a cylindrical member with an outer diameter smaller than the inner diameter of the axial hole 3f, and its outer end portion protrudes into a recess 3g on the outer side of the axial hole 3f. A male thread 36a is formed on the outer peripheral surface of the outer end portion of the stem portion 36. A fastening nut 37 that is inserted from the outer side of the axial hole 3f is threaded onto the male thread 36a of the stem portion 36.

[0050] The threaded surface of the fastening nut 37 abuts against the inner bottom surface of the recess 3g. As a result, the face spline 11a of the crimped portion 11 of the hub wheel 3 and the face spline 25a of the shoulder portion 25 of the outer joint member 21 are held in an engaged state, and torque from the drive shaft can be transmitted to the hub wheel 3 via the outer joint member 21.

[0051] The gap a between the stem portion 36 and the inner diameter of the axial hole 3f of the hub wheel 3 is formed to be larger than the sum of the gap d3 between the inner diameter of the cover member 17 and the outer diameter of the shoulder portion 25 of the constant velocity universal joint 20 and the length d4 from the inner diameter of the cover member 17 to the inner diameter side end of the face spline seal member 18.

[0052] By configuring it in this manner, it is possible to prevent the face spline sealing member 18 from coming into contact with the face spline 25a of the constant velocity universal joint 20 when assembling the constant velocity universal joint 20, thereby preventing damage to the face spline sealing member 18 during assembly.

[0053] (Fifth embodiment) As a fifth embodiment, as shown in FIG. 7, the outer diameter side end of the abutting portion 17a of the cover member 17 can be configured to be located on the outer diameter side of the outer diameter side end of the face spline seal member 18.

[0054] As shown in FIG. 7, when the cover member 17 is clamped between the mating surface of the inner seal member 9 with the inner ring 4 and the outer diameter surface of the inner ring 4, the cover member 17 is pressed toward the outer side using a jig T.

[0055] The jig T may be configured to abut against a surface of the abutting portion 17a that is located on the outer diameter side of the outer diameter side end of the face spline seal member 18. In other words, the jig T is configured in an annular shape, and is configured so that the inner diameter width thereof is larger than the outer diameter side end of the face spline seal member 18.

[0056] By configuring it in this manner, the jig T does not come into contact with the face spline seal member 18 provided at the inner end of the cover member 17, so the cover member 17 can be easily pressed toward the outer side using the jig T.

[0057] (Sixth embodiment) 8 and 9, as a sixth embodiment, an expanded diameter portion can be provided in the cover cylindrical portion 17b of the cover member 17, and an inner contact surface 17d for the jig T can be provided on the inner end surface of the expanded diameter portion. The inner end surface of the expanded diameter portion is radially inclined perpendicular to the axial direction, and the portion including the inner end portion where the face spline seal member 18 is provided is formed in a stepped shape.

[0058] As shown in Figure 9, when the cover member 17 is clamped between the mating surface of the inner seal member 9 with the inner ring 4 and the outer diameter surface of the inner ring 4, the cover member 17 is pressed toward the outer side using a jig T.

[0059] The jig T may be configured to abut against the inner abutment surface 17d for the jig T. That is, the jig T is configured to be annular, and its outer diameter width is configured to be smaller than the inner peripheral surface of the expanded diameter portion of the cover tubular portion 17b.

[0060] By configuring it in this manner, the jig T does not come into contact with the face spline seal member 18 provided at the inner end of the cover member 17, so the cover member 17 can be easily pressed toward the outer side using the jig T.

[0061] While the wheel bearing device here is exemplified as being constituted by a double-row angular contact ball bearing using balls 7 as rolling elements, the present invention is not limited to this and may also be a double-row tapered roller bearing using tapered rollers as rolling elements. Furthermore, as long as the wheel bearing device according to the present invention is of the inner ring rotating type, it may have, in addition to the exemplified third-generation structure, for example, a so-called second-generation structure in which a pair of inner rings are press-fitted into a small-diameter stepped portion of the hub ring, or a fourth-generation structure in which inner rolling surfaces are formed directly on the outer peripheries of the hub ring and the outer joint member of a constant velocity universal joint.

[0062] (Seventh embodiment) In a seventh embodiment, as shown in FIG. 10 , a configuration may be adopted in which the hub ring 3 is not provided with a crimped portion, but rather a face spline 4b is provided on the inner end surface of the inner ring 4. The inner end surface of the inner ring 4 on which the face spline 4b is formed is formed further inward than the inner end surface of the hub ring 3. The face spline 4b is formed on a portion of the inner diameter side of the inner end surface of the inner ring 4, and is equipped with a plurality of protruding portions protruding from the inner end surface of the inner ring 4 and a plurality of recessed portions provided between the protruding portions. The protruding portions and recessed portions each extend radially and are arranged alternately along the circumferential direction. The face spline 4b engages with a face spline 25a provided on the shoulder portion 25.

[0063] Furthermore, the cover tubular portion 17b of the cover member 17 covers the fitting portion between the face spline 4b and the face spline 25a. With this configuration, the cover member 17 can more easily prevent dust from entering the fitting portion between the face spline 4b and the face spline 25a from the outside, improving maintainability.

[0064] Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments, which are merely examples, and it goes without saying that the present invention can be embodied in various other forms without departing from the spirit of the present invention. The scope of the present invention is indicated by the claims, and further includes the equivalent meanings set forth in the claims, and all modifications within the scope of the claims. [Explanation of symbols]

[0065] 1 Wheel bearing device 2 Outer ring (outer member) 2c・2d Outer raceway groove (outer raceway surface) 3 Hub ring (inner part) 3c・Inner raceway groove (inner raceway surface) 4 Inner ring (inner part) 4a Inner raceway groove (inner raceway surface) 5 Inner ball row 6 Outer ball row 7 Ball 8 Cage 9 Inner seal member 10 Outer seal member 11 Fastening section 11a Face Spline 17 Cover member 17a Contact part 17b Cover cylinder 17c Engagement protrusion 17d Inner contact surface 18 Face spline seal member 18 18a First Lip 18b Second Lip 20 Constant velocity universal joint 25 Shoulder 25a Face Spline T jig

Claims

1. an outer member having an outer raceway surface on its inner periphery; an inner member having an inner raceway surface facing the outer raceway surface; a rolling element accommodated between the outer raceway surface and the inner raceway surface so as to be able to roll freely; a constant velocity universal joint connected to the inner member; a seal member that seals between the outer member and the inner member; A wheel bearing device comprising: a face spline is formed on an inner side end surface of the inner member and on a shoulder portion of the constant velocity universal joint, a cover member for protecting an outer diameter side of the face spline; The inner diameter of the cover member is formed to increase toward the inner side. A wheel bearing device characterized in that:

2. the cover member has a cylindrical cover portion that covers the shoulder portion of the constant velocity universal joint, and the inner diameter of the cylindrical cover portion is greater than 100% and less than 103% of the outer diameter of the shoulder portion of the constant velocity universal joint.

2. The wheel bearing device according to claim 1.

3. a face spline seal member that is in sliding contact with the outer peripheral surface of the shoulder portion is provided at an inner end of the cover member; The face spline seal member is made of an elastic material, The face spline seal member has a lip.

2. The wheel bearing device according to claim 1.

4. a recess is provided on the outer diameter of the constant velocity universal joint; An engaging protrusion that engages with the recess is provided on the inner diameter of the cover member.

4. The wheel bearing device according to claim 3.

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