JP6767810B2 - Bearing device for wheels - Google Patents

Description

The present invention relates to a wheel bearing device.

Conventionally, a wheel bearing device that rotatably supports a wheel in a suspension device such as an automobile has been known. In the wheel bearing device, an outer member is fixed to a knuckle constituting the suspension device. Further, in the wheel bearing device, an inner member is arranged inside the outer member, and a rolling element is interposed between the outer member and the inner member. In this way, the wheel bearing device constitutes a rolling bearing structure and makes the wheels attached to the inner members rotatable.

By the way, in such a wheel bearing device, when muddy water or dust enters the annular space formed between the outer member and the inner member, the rolling elements are damaged and the bearing life is shortened. Further, even if the grease sealed in the annular space leaks, the rolling elements are damaged and the bearing life is shortened. Therefore, the wheel bearing device includes a sealing member that seals the annular space in order to prevent the intrusion of muddy water and dust and the leakage of grease. For example, as described in Patent Document 1 and Patent Document 2.

The wheel bearing device described in Patent Document 1 includes an outer member, an inner member, a rolling element interposed between the outer member and the inner member, and between the outer member and the inner member. It includes a sealing member that seals the formed annular space. However, in such a wheel bearing device, when muddy water travels through the outer member and reaches the seal member (see arrow F shown in FIG. 13 (A)), the seal member is damaged by biting foreign matter contained in the muddy water. There was a concern that it would wear out. That is, there is a concern that the sealing property (durability) of the sealing member will be lowered.

Therefore, the wheel bearing device described in Patent Document 2 includes a weir member that is externally fitted to the outer member so as to prevent muddy water from traveling through the outer member and reaching the seal member. However, in such a wheel bearing device, muddy water may get over the weir member and reach the seal member (see arrow F shown in FIG. 13B), and there is a concern that the seal member may be damaged or worn. There was a problem that it could not be wiped out. That is, there is a problem that the concern that the sealing property (durability) of the sealing member is lowered cannot be eliminated.

In addition, it is known that when the vehicle body is turning, the radial load and the axial load applied to the wheels outside the turning direction (the left wheel in the case of right turning and the right wheel in the case of left turning) increase. .. Then, the outer end of the outer member may be deformed into an elliptical shape, and there is also a problem that the weir member is pulled out by repeating such deformation.

Further, the wheel mounting flange of the inner member is provided with a plurality of bolt holes on a concentric circle centered on the rotation axis of the inner member, and hub bolts are press-fitted into each bolt hole. Each hub bolt is arranged with its head close to the outer member. Therefore, if the height dimension of the weir member is increased in consideration of making it difficult for muddy water to get over, there is also a problem that the weir member becomes an obstacle and the hub bolt cannot be replaced.

Japanese Unexamined Patent Publication No. 2014-219100 Japanese Unexamined Patent Publication No. 2011-7272

An object of the present invention is to provide a wheel bearing device capable of preventing muddy water from traveling through an outer member and reaching a seal member. Another object of the present invention is to provide a wheel bearing device in which the weir member, which is a component of the present invention, is hard to come off even if the outer member is repeatedly deformed, and does not become an obstacle when the hub bolt is replaced.

That is, the present invention integrally has an outer member in which a double row of outer rolling surfaces are integrally formed on the inner circumference and a wheel mounting flange into which a plurality of hub bolts are press-fitted, and has a small diameter extending axially to the outer circumference. It consists of a hub wheel on which a step portion is formed and at least one inner ring press-fitted into the small-diameter step portion of the hub wheel, and has a double-row inner rolling surface facing the outer rolling surface of the double-row on the outer circumference. The formed inner member, a double-row rolling element rotatably interposed between the rolling surfaces of the outer member and the inner member, and the outer member and the inner member. In a wheel bearing device provided with a seal member internally fitted to the outer member so as to close the outer end of the annular space formed between the two, the portion of the portion in which the seal member is internally fitted. On the outer diameter side, a dam member that is externally fitted to the outer member is provided, and the dam member has two standing plate portions extending outward in the radial direction, and the standing plate portion and the outer portion on the inner side. The standing plate portions on the side are arranged side by side with a predetermined gap.

In the wheel bearing device according to the present invention, the height dimension of the standing plate portion on the inner side is larger than the height dimension of the standing plate portion on the outer side.

In the wheel bearing device according to the present invention, the height dimension of the standing plate portion on the outer side is larger than the height dimension of the standing plate portion on the inner side.

In the wheel bearing device according to the present invention, the outer edge portion of the standing plate portion on the outer side is bent toward the outer side to cover the gap portion between the wheel mounting flange and the outer member.

In the wheel bearing device according to the present invention, the plurality of hub bolts are arranged on concentric circles centered on the rotation axis of the inner member in the same phase with each other, and the standing plate portion on the outer side and the above on the inner side. One or both of the standing plate portions are formed with guide grooves for passing the hub bolts.

In the wheel bearing device according to the present invention, the guide grooves are formed in the same number or multiples as the hub bolts and in the same phases on the concentric circles.

In the wheel bearing device according to the present invention, a vertical direction line that intersects the rotation axis and is parallel to the direction in which gravity acts, and a front-rear direction line that also intersects the rotation axis and is perpendicular to the vertical direction line. Assuming that, the guide groove is formed so as not to intersect the front-rear direction line.

As the effect of the present invention, the following effects are exhibited.

That is, the wheel bearing device according to the present invention includes a weir member that is externally fitted to the outer member on the outer diameter side of the portion where the seal member is internally fitted. The weir member has two standing plate portions extending outward in the radial direction, and the standing plate portion on the inner side and the standing plate portion on the outer side are arranged side by side with a predetermined gap. As a result, in the bearing device for this wheel, the standing plate portion on the inner side and the standing plate portion on the outer side, which form the weir member, each block the muddy water, so that the muddy water reaches the seal member through the outer member. Can be prevented. Therefore, it is possible to eliminate the concern that the sealing property (durability) of the sealing member is lowered, and it is possible to prevent damage to the rolling element and improve the bearing life. Further, since the fitting surface pressure is increased at two locations, that is, the standing plate portion on the inner side and the standing plate portion on the outer side, it is possible to prevent the weir member from coming off.

In the wheel bearing device according to the present invention, the height dimension of the standing plate portion on the inner side is larger than the height dimension of the standing plate portion on the outer side. As a result, in the bearing device for this wheel, the fitting surface pressure of the portion corresponding to the standing plate portion on the inner side where the amount of deformation of the outer member is relatively small increases, so that the weir member can be further prevented from coming off. Can be done.

In the wheel bearing device according to the present invention, the height dimension of the standing plate portion on the outer side is larger than the height dimension of the standing plate portion on the inner side. As a result, in the bearing device for this wheel, the fitting surface pressure of the portion corresponding to the standing plate portion on the outer side where the amount of deformation of the outer member is relatively large increases, so that the outer member is restrained and exceeds a certain level. Deformation can be suppressed.

In the wheel bearing device according to the present invention, the outer edge portion of the standing plate portion on the outer side is bent toward the outer side to cover the gap portion between the wheel mounting flange and the outer member. As a result, in the bearing device for wheels, the standing plate portion on the outer side receives the droplets of muddy water and the floating dust, so that the droplets of the muddy water and the floating dust can be prevented from reaching the seal member. Therefore, it is possible to further prevent damage to the rolling elements and improve the bearing life.

In the wheel bearing device according to the present invention, a plurality of hub bolts are arranged on concentric circles centered on the rotation axis of the inner member in the same phase with each other, and the standing plate portion on the outer side and the standing plate portion on the inner side are arranged. One or both are formed with guide grooves for passing hub bolts. As a result, in the bearing device for this wheel, the hub bolt can be replaced without disassembling the outer member and the inner member.

In the wheel bearing device according to the present invention, the guide grooves are formed in the same number or multiples as the hub bolts and on concentric circles in the same phase. As a result, in the bearing device for this wheel, all the hub bolts can be overlapped with all the guide grooves, so that the hub bolts can be easily replaced.

In the wheel bearing device according to the present invention, a vertical direction line that intersects the rotation axis and is parallel to the direction in which gravity acts, and a front-rear direction line that also intersects the rotation axis and is perpendicular to the vertical direction line. Assumed, the guide groove is formed so as not to intersect the front-rear direction line. As a result, even if the outer member of the bearing device for wheels is deformed so as to expand in the vertical direction, the rigidity of the weir member in the front-rear direction is secured and the fitting surface pressure is maintained. Can be prevented from coming off.

The perspective view which shows the whole structure of the bearing device for a wheel. The cross-sectional view which shows the whole structure of the bearing device for a wheel. An enlarged cross-sectional view showing a partial structure of a wheel bearing device. An enlarged cross-sectional view showing a partial structure of a wheel bearing device. An enlarged cross-sectional view showing a weir member according to the first embodiment. The figure which shows the replacement work of a hub bolt. The enlarged sectional view which shows the weir member which concerns on 2nd Embodiment. The figure which shows the replacement work of a hub bolt. An enlarged cross-sectional view showing a weir member according to a third embodiment. The figure which shows the replacement work of a hub bolt. An enlarged cross-sectional view showing a weir member according to another embodiment. An enlarged cross-sectional view showing a weir member according to another embodiment. FIG. 5 is a cross-sectional view showing a partial structure of a conventional wheel bearing device.

Hereinafter, the wheel bearing device 1 according to the present invention will be described with reference to FIGS. 1 to 4. Note that FIG. 2 is a cross-sectional view taken along the line AA in FIG. 3 and 4 are enlarged views of a part of the region in FIG.

The wheel bearing device 1 rotatably supports wheels in a suspension device such as an automobile. The wheel bearing device 1 includes an outer member 2, an inner member 3 (hub wheel 4 and inner ring 5), a rolling element 6, a seal member 7 (hereinafter referred to as “one-side seal member 7”), and a seal member 10 (hereinafter referred to as “one-side seal member 7”). "Other side seal member 10") is provided. In the following, "one side" means the vehicle body side of the wheel bearing device 1, that is, the inner side. Further, the “other side” represents the wheel side of the wheel bearing device 1, that is, the outer side.

The outer member 2 supports the inner member 3 (hub ring 4 and inner ring 5). The outer member 2 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C formed in a substantially cylindrical shape. A diameter-expanded portion 2a is formed at the inner end of the outer member 2. Further, an enlarged diameter portion 2b is formed at the outer side end portion of the outer member 2. Further, on the inner circumference of the outer member 2, the outer rolling surface 2c and the outer rolling surface 2d are formed in an annular shape so as to be parallel to each other. The outer rolling surface 2c and the outer rolling surface 2d are induction hardened and hardened so that the surface hardness is in the range of 58 to 64 HRC. A knuckle mounting flange 2e for mounting on the knuckle constituting the suspension device is integrally formed on the outer periphery of the outer member 2. A weir member 20, which will be described later, is fitted on the outer periphery of the outer member 2.

The inner member 3 rotatably supports a wheel (not shown). The inner member 3 is composed of a hub ring 4 and an inner ring 5.

The hub ring 4 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C formed in a substantially cylindrical shape. A small diameter step portion 4a is formed at the inner end portion of the hub ring 4. The inner ring 5 is press-fitted into the small diameter step portion 4a. Further, the small diameter step portion 4a is formed with a crimped portion 4b of the inner ring 5 by bending the inner end portion thereof outward in the radial direction. Further, a wheel mounting flange 4c is integrally formed on the outer periphery of the hub wheel 4. The wheel mounting flange 4c is provided with bolt holes 4d at equal intervals on a concentric circle centered on the rotation axis L of the inner member 3, and hub bolts 40 are press-fitted into the respective bolt holes 4d. Further, an inner rolling surface 4e is formed in an annular shape on the outer circumference of the hub ring 4. The hub ring 4 is induction hardened from the small diameter step portion 4a through the inner rolling surface 4e to the seal land portion (composed of the shaft surface portion 4f, the curved surface portion 4g, and the side surface portion 4h described later), and the surface hardness is reduced. It is hardened so as to be in the range of 58 to 64 HRC. As a result, the hub wheel 4 has sufficient mechanical strength and durability against the rotational bending load applied to the wheel mounting flange 4c. The inner rolling surface 4e faces the outer rolling surface 2d of the outer member 2.

The inner ring 5 is made of high carbon chrome bearing steel such as SUJ2 formed in a substantially cylindrical shape. An inner rolling surface 5a is formed in an annular shape on the outer circumference of the inner ring 5. That is, the inner ring 5 is press-fitted into the small-diameter step portion 4a of the hub ring 4, and forms an inner rolling surface 5a on the outer periphery of the small-diameter step portion 4a. The inner ring 5 is so-called sub-quenched and hardened so as to have a core portion in the range of 58 to 64 HRC. As a result, the inner ring 5 has sufficient mechanical strength and durability against the rotational bending load applied to the wheel mounting flange 4c. The inner rolling surface 5a faces the outer rolling surface 2c of the outer member 2.

The rolling element 6 is interposed between the outer member 2 and the inner member 3 (hub ring 4 and inner ring 5). The rolling element 6 has a ball row 6a on the inner side (hereinafter referred to as “one side ball row 6a”) and a ball row 6b on the outer side (hereinafter referred to as “other side ball row 6b”). The one-side ball row 6a and the other-side ball row 6b are made of high carbon chrome bearing steel such as SUJ2. The one-side ball row 6a and the other-side ball row 6b are so-called stub-quenched and hardened so as to have a core portion in the range of 58 to 64 HRC. In the one-side ball row 6a, a plurality of balls are held in an annular shape by a cage. The one-side ball row 6a is rotatably accommodated between the inner rolling surface 5a formed on the inner ring 5 and the outer rolling surface 2c of the outer member 2 facing the inner rolling surface 5a. In the other side ball row 6b, a plurality of balls are held in an annular shape by a cage. The other side ball row 6b is rotatably accommodated between the inner rolling surface 4e formed on the hub wheel 4 and the outer rolling surface 2d of the outer member 2 facing the inner rolling surface 4e. In this way, the one-side ball row 6a and the other-side ball row 6b are composed of the outer member 2 and the inner member 3 (hub ring 4 and inner ring 5) to form a double-row angular contact ball bearing. The wheel bearing device 1 is a wheel bearing device having a third generation structure in which the inner rolling surface 4e of the other side ball row 6b is formed on the outer periphery of the hub wheel 4, but the present invention is not limited to this. The second generation structure in which a pair of inner rings 5 are press-fitted and fixed to the hub wheel 4, and the first generation composed of an outer ring which is an outer member 2 and an inner ring which is an inner member 3 without the hub wheel 4. It may be a structure.

The one-side seal member 7 is attached to the inner end portion of the annular space S formed between the outer member 2 and the inner member 3. The one-side seal member 7 is composed of an annular seal ring 8 and an annular slinger 9.

The seal ring 8 is fitted (innerly fitted) to the enlarged diameter portion 2a of the outer member 2 and is integrally formed with the outer member 2. The seal ring 8 has a core metal 81 and a seal rubber 82 which is an elastic member.

The core metal 81 is a ferritic stainless steel sheet (JIS standard SUS430 series, etc.), an austenitic stainless steel sheet (JIS standard SUS304 series, etc.), or a rust-preventive cold-rolled steel sheet (JIS standard SPCC series, etc.). It is composed of. In the core metal 81, an annular steel plate is bent by press working, and the axial cross section is formed in a substantially L shape. As a result, the core metal 81 is formed with a cylindrical fitting portion 81a and a disc-shaped side plate portion 81b extending from one end thereof toward the inner member 3 (inner ring 5). The fitting portion 81a and the side plate portion 81b intersect each other substantially vertically, and the fitting portion 81a faces the fitting portion 9a of the slinger 9 described later. Further, the side plate portion 81b faces the side plate portion 9b of the slinger 9 described later. A seal rubber 82, which is an elastic member, is vulcanized and adhered to the fitting portion 81a and the side plate portion 81b.

The seal rubber 82 includes NBR (acrylonitrile-butadiene rubber), HNBR (hydrogenated acrylonitrile butadiene rubber) with excellent heat resistance, EPDM (ethylene propylene rubber), ACM (polyacrylic rubber) with excellent heat resistance and chemical resistance. It is composed of synthetic rubber such as FKM (fluorine rubber) or silicon rubber. The seal rubber 82 is formed with a radial lip 82a, an inner axial lip 82b, and an outer axial lip 82c, which are seal lips.

The slinger 9 is fitted to the outer circumference of the inner member 3 (outer circumference of the inner ring 5) and is integrally formed with the inner member 3.

The slinger 9 is a ferritic stainless steel sheet (JIS standard SUS430 series, etc.), an austenitic stainless steel sheet (JIS standard SUS304 series, etc.), or a rust-preventive cold-rolled steel sheet (JIS standard SPCC series, etc.). It is configured. In the slinger 9, an annular steel plate is bent by press working, and the axial cross section is formed in a substantially L shape. As a result, the slinger 9 is formed with a cylindrical fitting portion 9a and a disc-shaped side plate portion 9b extending from the end portion thereof toward the outer member 2. The fitting portion 9a and the side plate portion 9b intersect each other perpendicularly, and the fitting portion 9a faces the fitting portion 81a of the seal ring 8 described above. Further, the side plate portion 9b faces the side plate portion 81b of the seal ring 8 described above. A magnetic encoder 9c is provided on the side plate portion 9b.

The one-side seal member 7 is arranged so that the seal ring 8 and the slinger 9 face each other. At this time, the radial lip 82a comes into contact with the fitting portion 9a of the slinger 9 via the oil film. Further, the inner axial lip 82b comes into contact with the side plate portion 9b of the slinger 9 via the oil film. Then, the outer axial lip 82c also comes into contact with the side plate portion 9b of the slinger 9 via the oil film. In this way, the one-side sealing member 7 constitutes a so-called pack seal to prevent the intrusion of muddy water and dust and the leakage of grease.

The other side seal member 10 is attached to the outer side end portion of the annular space S formed between the outer member 2 and the inner member 3. The other side seal member 10 is composed of an annular seal ring 11.

The other side seal member 10 is fitted (innerly fitted) to the enlarged diameter portion 2b of the outer member 2 and is integrally formed with the outer member 2. The seal ring 11 has a core metal 111 and a seal rubber 112 which is an elastic member.

The core metal 111 is a ferritic stainless steel sheet (JIS standard SUS430 series, etc.), an austenitic stainless steel sheet (JIS standard SUS304 series, etc.), or a rust-preventive cold-rolled steel sheet (JIS standard SPCC series, etc.). It is composed of. The core metal 111 is formed by bending an annular steel plate by press working to form a substantially C shape in an axial cross-sectional view. As a result, the core metal 111 is formed with a cylindrical fitting portion 111a and a disc-shaped side plate portion 111b extending from one end thereof toward the inner member 3 (hub ring 4). The fitting portion 111a and the side plate portion 111b intersect with each other while being curved, and the fitting portion 111a faces the shaft surface portion 4f of the hub ring 4. Further, the side plate portion 111b faces the curved surface portion 4g and the side surface portion 4h (pointing to the end surface of the wheel mounting flange 4c) of the hub wheel 4. A seal rubber 112, which is an elastic member, is vulcanized and adhered to the side plate portion 111b.

The seal rubber 112 includes NBR (acrylonitrile-butadiene rubber), HNBR (hydrogenated acrylonitrile butadiene rubber) with excellent heat resistance, EPDM (ethylene propylene rubber), ACM (polyacrylic rubber) with excellent heat resistance and chemical resistance. It is composed of synthetic rubber such as FKM (fluorine rubber) or silicon rubber. The seal rubber 112 is formed with a radial lip 112a, an inner axial lip 112b, and an outer axial lip 112c, which are seal lips.

The other side seal member 10 is arranged so that the seal ring 11 and the hub ring 4 face each other. At this time, the radial lip 112a comes into contact with the shaft surface portion 4f of the hub ring 4 via the oil film. Further, the axial lip 112b comes into contact with the curved surface portion 4g of the hub ring 4 via the oil film. Then, the outer axial lip 112c also comes into contact with the side surface portion 4h of the hub ring 4 via the oil film. In this way, the other side sealing member 10 prevents the intrusion of muddy water and dust and prevents the leakage of grease.

Next, the weir member 20 according to the first embodiment will be described in detail with reference to FIGS. 5 and 6. FIG. 5A is an enlarged view of the region R in FIG. 2, and FIG. 5B is a diagram showing a cross section taken along the line BB in FIG. Note that FIG. 6 shows the replacement work of the hub bolt 40.

The dam member 20 according to the first embodiment is a ferritic stainless steel plate (JIS standard SUS430 series or the like), an austenitic stainless steel plate (JIS standard SUS304 series or the like), or a cold rolled steel plate (JIS) that has been rust-proofed. It is composed of standard SPCC series, etc.). The weir member 20 is formed by bending an annular steel plate by press working to form a substantially U-shape in an axial cross-sectional view. As a result, the weir member 20 has a cylindrical fitting portion 20a, a standing plate portion 20b extending radially outward from the inner side end portion thereof, and a standing plate portion 20b extending radially outward from the outer side end portion thereof. The plate portion 20c and the plate portion 20c are formed. The fitting portion 20a and the standing plate portion 20b intersect with each other substantially vertically, and the fitting portion 20a and the standing plate portion 20c also intersect with each other substantially vertically. Therefore, the standing plate portion 20b and the standing plate portion 20c are arranged in parallel with each other with a predetermined gap. In the weir member 20 according to the first embodiment, the height dimension Db of the standing plate portion 20b on the inner side is larger than the height dimension Dc of the standing plate portion 20c on the outer side (Db> Dc). ). Further, the gap dimension Da between the standing plate portion 20b and the standing plate portion 20c is substantially equal to the height dimension Db of the standing plate portion 20b (Da≈Db). The gap dimension Da and the height dimension Db are at least 5 mm or more.

With such a design, in the bearing device 1 for this wheel, the standing plate portion 20b on the inner side and the standing plate portion 20c on the outer side, which constitute the weir member 20, each block the muddy water, so that the muddy water is outward. It is possible to prevent the seal member 10 from reaching the other side through the member 2. More specifically, the standing plate portion 20b on the inner side dams a part of the muddy water that has been transmitted, and the standing plate portion 20c on the outer side dams the muddy water that has passed over the standing plate portion 20b, so that the muddy water is outward. It is possible to prevent the seal member 10 from reaching the other side through the member 2. Therefore, it is possible to eliminate the concern that the sealing property (durability) of the other side sealing member 10 is lowered, and thus prevent damage to the rolling elements 6 (one side ball row 6a and the other side ball row 6b) to improve the bearing life. realizable.

In addition, in the weir member 20, since the standing plate portion 20b on the inner side extends outward in the radial direction, the rigidity at the inner side end portion is high with respect to the load applied in the radial direction. Further, since the standing plate portion 20c on the outer side also extends outward in the radial direction, the rigidity at the end portion on the outer side is also high with respect to the load applied in the radial direction. Therefore, since the fitting surface pressure increases at two locations, the standing plate portion 20b on the inner side and the portion corresponding to the standing plate portion 20c on the outer side (see the surface pressure distribution P), it is possible to prevent the weir member 20 from coming off. it can. More specifically, due to the fact that the height dimension Db of the standing plate portion 20b is larger than the height dimension Dc of the standing plate portion 20c, it is more than the fitting surface pressure of the portion corresponding to the standing plate portion 20c on the outer side. Also, the fitting surface pressure of the portion corresponding to the standing plate portion 20b on the inner side is larger (see the surface pressure distribution P). Then, the fitting surface pressure of the portion corresponding to the standing plate portion 20b on the inner side where the deformation amount of the outer member 2 is relatively small increases, so that the weir member 20 can be further prevented from coming off. In particular, since the weir member 20 is externally fitted to the outer member 2 on the outer diameter side of the portion where the other side seal member 10 is internally fitted, it is possible to further prevent the weir member 20 from coming off. This is because the other side seal member 10 is stretched in the deformation direction in which the outer member 2 contracts, and the weir member 20 is restrained in the deformation direction in which the outer member 2 expands.

In addition, the main weir member 20 has a guide groove 20d for the hub bolt 40 formed on the outer edge of the standing plate portion 20b. More specifically, the outer edge portion of the standing plate portion 20b is cut out in an arc shape to form a guide groove 20d for passing the hub bolt 40.

With such a design, the bearing device 1 for this wheel can be combined with the outer member 2 even if the height dimension Db of the standing plate portion 20b on the inner side is increased in consideration of making it difficult for muddy water to get over. The hub bolt 40 can be replaced without disassembling the inner member 3.

In addition, the wheel bearing device 1 has five hub bolts 40, each of which is provided at a position where the phase angle about the rotation axis L is 72 °. Therefore, the standing plate portion 20b of the weir member 20 is formed with five guide grooves 20d in the circumferential direction at positions where the phase angle about the rotation axis L is 72 °. However, guide grooves 20d may be provided at 10 places which are multiples. At this time, the guide grooves 20d are formed at positions where the phase angle about the rotation axis L is 36 °. Further, although the wheel bearing device 1 has five hub bolts 40, for example, it is assumed that the wheel bearing device 1 has four hub bolts 40 and is provided at a position where the phase angle about the rotation axis L is 90 °. Is also good. In this case, the four guide grooves 20d are formed at positions where the phase angle about the rotation axis L is 90 °. However, guide grooves 20d may be provided at eight locations that are multiples.

With such a design, the bearing device 1 for this wheel can superimpose the positions of all the hub bolts 40 on all the guide grooves 20d, so that the hub bolts 40 can be easily replaced.

It is assumed that the vertical direction line La intersects the rotation axis L and is parallel to the direction in which gravity acts, and the direction that intersects the rotation axis L and is perpendicular to the vertical direction line is the front-rear direction line Lb. In this case, the guide groove 20d is formed so as not to intersect the front-rear direction line Lb.

With such a design, even if the outer member 2 is deformed so as to expand in the vertical direction, the rigidity of the weir member 20 in the front-rear direction is ensured and the fitting surface pressure of the bearing device 1 for this wheel is secured. Is maintained, so that the weir member 20 can be further prevented from coming off.

Next, the weir member 20 according to the second embodiment will be described in detail with reference to FIGS. 7 and 8. FIG. 7 (A) corresponds to an enlarged view of the region R in FIG. 2, and FIG. 7 (B) corresponds to a view showing a BB cross section in FIG. Note that FIG. 8 shows the replacement work of the hub bolt 40.

The dam member 20 according to the second embodiment is a ferritic stainless steel plate (JIS standard SUS430 series or the like), an austenitic stainless steel plate (JIS standard SUS304 series or the like), or a cold rolled steel plate (JIS) that has been rust-proofed. It is composed of standard SPCC series, etc.). The weir member 20 is formed by bending an annular steel plate by press working to form a substantially U-shape in an axial cross-sectional view. As a result, the weir member 20 has a cylindrical fitting portion 20a, a standing plate portion 20b extending radially outward from the inner side end portion thereof, and a standing plate portion 20b extending radially outward from the outer side end portion thereof. The plate portion 20c and the plate portion 20c are formed. The fitting portion 20a and the standing plate portion 20b intersect with each other substantially vertically, and the fitting portion 20a and the standing plate portion 20c also intersect with each other substantially vertically. Therefore, the standing plate portion 20b and the standing plate portion 20c are arranged in parallel with each other with a predetermined gap. In the weir member 20 according to the second embodiment, the height dimension Dc of the outer side standing plate portion 20c is larger than the height dimension Db of the inner side standing plate portion 20b (Db <Dc). ). Further, the gap dimension Da between the standing plate portion 20b and the standing plate portion 20c is substantially equal to the height dimension Dc of the standing plate portion 20c (Da≈Dc). The gap dimension Da and the height dimension Dc are at least 5 mm or more.

With such a design, in the bearing device 1 for this wheel, the standing plate portion 20b on the inner side and the standing plate portion 20c on the outer side, which constitute the weir member 20, each block the muddy water, so that the muddy water is outward. It is possible to prevent the seal member 10 from reaching the other side through the member 2. More specifically, the standing plate portion 20b on the inner side dams a part of the muddy water that has been transmitted, and the standing plate portion 20c on the outer side dams the muddy water that has passed over the standing plate portion 20b, so that the muddy water is outward. It is possible to prevent the seal member 10 from reaching the other side through the member 2. Therefore, it is possible to eliminate the concern that the sealing property (durability) of the other side sealing member 10 is lowered, and thus prevent damage to the rolling elements 6 (one side ball row 6a and the other side ball row 6b) to improve the bearing life. realizable.

In addition, in the weir member 20, since the standing plate portion 20b on the inner side extends outward in the radial direction, the rigidity at the inner side end portion is high with respect to the load applied in the radial direction. Further, since the standing plate portion 20c on the outer side also extends outward in the radial direction, the rigidity at the end portion on the outer side is also high with respect to the load applied in the radial direction. Therefore, since the fitting surface pressure increases at two locations, the standing plate portion 20b on the inner side and the portion corresponding to the standing plate portion 20c on the outer side (see the surface pressure distribution P), it is possible to prevent the weir member 20 from coming off. it can. More specifically, due to the fact that the height dimension Dc of the standing plate portion 20c is larger than the height dimension Db of the standing plate portion 20b, it is more than the fitting surface pressure of the portion corresponding to the standing plate portion 20b on the inner side. However, the fitting surface pressure of the portion corresponding to the standing plate portion 20c on the outer side is larger (see the surface pressure distribution P). Then, the fitting surface pressure of the portion corresponding to the standing plate portion 20c on the outer side where the amount of deformation of the outer member 2 is relatively large increases, so that the outer member 2 is restrained to suppress the deformation beyond a certain level. Can be done. In particular, since the weir member 20 is externally fitted to the outer member 2 on the outer diameter side of the portion where the other side seal member 10 is internally fitted, the deformation of the outer member 2 can be further suppressed. This is because the other side seal member 10 is stretched in the deformation direction in which the outer member 2 contracts, and the weir member 20 is restrained in the deformation direction in which the outer member 2 expands.

In addition, the main weir member 20 has a guide groove 20d for the hub bolt 40 formed on the outer edge of the standing plate portion 20c. More specifically, the outer edge portion of the standing plate portion 20c is cut out in an arc shape to form a guide groove 20d for passing the hub bolt 40.

With such a design, the bearing device 1 for this wheel can be combined with the outer member 2 even if the height dimension Dc of the standing plate portion 20c on the outer side is increased in consideration of making it difficult for muddy water to get over. The hub bolt 40 can be replaced without disassembling the inner member 3.

In addition, the wheel bearing device 1 has five hub bolts 40, each of which is provided at a position where the phase angle about the rotation axis L is 72 °. Therefore, the standing plate portion 20c of the weir member 20 is formed with five guide grooves 20d in the circumferential direction at positions where the phase angle about the rotation axis L is 72 °. However, guide grooves 20d may be provided at 10 places which are multiples. At this time, the guide grooves 20d are formed at positions where the phase angle about the rotation axis L is 36 °. Further, although the wheel bearing device 1 has five hub bolts 40, for example, it is assumed that the wheel bearing device 1 has four hub bolts 40 and is provided at a position where the phase angle about the rotation axis L is 90 °. Is also good. In this case, the four guide grooves 20d are formed at positions where the phase angle about the rotation axis L is 90 °. However, guide grooves 20d may be provided at eight locations that are multiples.

With such a design, the bearing device 1 for this wheel can superimpose the positions of all the hub bolts 40 on all the guide grooves 20d, so that the hub bolts 40 can be easily replaced.

It is assumed that the vertical direction line La intersects the rotation axis L and is parallel to the direction in which gravity acts, and the direction that intersects the rotation axis L and is perpendicular to the vertical direction line is the front-rear direction line Lb. In this case, the guide groove 20d is formed so as not to intersect the front-rear direction line Lb.

With such a design, even if the outer member 2 is deformed so as to expand in the vertical direction, the rigidity of the weir member 20 in the front-rear direction is ensured and the fitting surface pressure of the bearing device 1 for this wheel is secured. Is maintained, so that the weir member 20 can be further prevented from coming off.

Next, the weir member 20 according to the third embodiment will be described in detail with reference to FIGS. 9 and 10. FIG. 9A corresponds to an enlarged view of the region R in FIG. 2, and FIG. 9B corresponds to a diagram showing a cross section taken along the line BB in FIG. Note that FIG. 10 shows the replacement work of the hub bolt 40.

The dam member 20 according to the third embodiment is a ferritic stainless steel plate (JIS standard SUS430 series or the like), an austenitic stainless steel plate (JIS standard SUS304 series or the like), or a cold rolled steel plate (JIS) that has been rust-proofed. It is composed of standard SPCC series, etc.). The weir member 20 is formed by bending an annular steel plate by press working to form a substantially U-shape in an axial cross-sectional view. As a result, the weir member 20 has a cylindrical fitting portion 20a, a standing plate portion 20b extending radially outward from the inner side end portion thereof, and a standing plate portion 20b extending radially outward from the outer side end portion thereof. The plate portion 20c and the plate portion 20c are formed. The fitting portion 20a and the standing plate portion 20b intersect with each other substantially vertically, and the fitting portion 20a and the standing plate portion 20c also intersect with each other substantially vertically. Therefore, the standing plate portion 20b and the standing plate portion 20c are arranged in parallel with each other with a predetermined gap. In the weir member 20 according to the third embodiment, the height dimensions Db and Dc of the inner side standing plate portion 20b and the outer side standing plate portion 20c are the same (Db = Dc). Further, the gap dimension Da between the standing plate portion 20b and the standing plate portion 20c is substantially equal to the height dimension Db of the standing plate portion 20b and the height dimension Dc of the standing plate portion 20c (Da≈Db, Dc). The gap dimension Da and the height dimensions Db / Dc are at least 5 mm or more.

With such a design, in the bearing device 1 for this wheel, the standing plate portion 20b on the inner side and the standing plate portion 20c on the outer side, which constitute the weir member 20, each block the muddy water, so that the muddy water is outward. It is possible to prevent the seal member 10 from reaching the other side through the member 2. More specifically, the standing plate portion 20b on the inner side dams a part of the muddy water that has been transmitted, and the standing plate portion 20c on the outer side dams the muddy water that has passed over the standing plate portion 20b, so that the muddy water is outward. It is possible to prevent the seal member 10 from reaching the other side through the member 2. Therefore, it is possible to eliminate the concern that the sealing property (durability) of the other side sealing member 10 is lowered, and thus prevent damage to the rolling elements 6 (one side ball row 6a and the other side ball row 6b) to improve the bearing life. realizable.

In addition, in the weir member 20, since the standing plate portion 20b on the inner side extends outward in the radial direction, the rigidity at the inner side end portion is high with respect to the load applied in the radial direction. Further, since the standing plate portion 20c on the outer side also extends outward in the radial direction, the rigidity at the end portion on the outer side is also high with respect to the load applied in the radial direction. Therefore, since the fitting surface pressure increases at two locations, the standing plate portion 20b on the inner side and the portion corresponding to the standing plate portion 20c on the outer side (see the surface pressure distribution P), it is possible to prevent the weir member 20 from coming off. it can. More specifically, the fitting surface of the portion corresponding to the standing plate portion 20b on the inner side is caused by the fact that the height dimension Db of the standing plate portion 20b and the height dimension Dc of the standing plate portion 20c are the same. The pressure and the fitting surface pressure of the portion corresponding to the standing plate portion 20c on the outer side are the same (see the surface pressure distribution P). Then, since the fitting surface pressure of the portion corresponding to the standing plate portion 20b on the inner side where the amount of deformation of the outer member 2 is relatively small increases, it is possible to further prevent the weir member 20 from coming off, and at the same time, Since the fitting surface pressure of the portion corresponding to the standing plate portion 20c on the outer side where the amount of deformation of the outer member 2 is relatively large increases, the outer member 2 can be restrained and the deformation beyond a certain level can be suppressed. .. In particular, since the weir member 20 is externally fitted to the outer member 2 on the outer diameter side of the portion where the other side seal member 10 is internally fitted, these effects can be greatly obtained. This is because the other side seal member 10 is stretched in the deformation direction in which the outer member 2 contracts, and the weir member 20 is restrained in the deformation direction in which the outer member 2 expands.

In addition, the main weir member 20 has a guide groove 20d for the hub bolt 40 formed on the standing plate portion 20b and the outer edge portion of the standing plate portion 20c. More specifically, the standing plate portion 20b and the outer edge portion of the standing plate portion 20c are cut out in an arc shape to form a guide groove 20d for passing the hub bolt 40.

With such a design, the bearing device 1 for this wheel has height dimensions Db and Dc of the standing plate portion 20b on the inner side and the standing plate portion 20c on the outer side in consideration of making it difficult for muddy water to get over. Even if the size is increased, the hub bolt 40 can be replaced without disassembling the outer member 2 and the inner member 3.

In addition, the wheel bearing device 1 has five hub bolts 40, each of which is provided at a position where the phase angle about the rotation axis L is 72 °. Therefore, the standing plate portion 20b and the standing plate portion 20c of the weir member 20 are formed with five guide grooves 20d in the circumferential direction at positions where the phase angle about the rotation axis L is 72 °. .. However, guide grooves 20d may be provided at 10 places which are multiples. At this time, the guide grooves 20d are formed at positions where the phase angle about the rotation axis L is 36 °. Further, although the wheel bearing device 1 has five hub bolts 40, for example, it is assumed that the wheel bearing device 1 has four hub bolts 40 and is provided at a position where the phase angle about the rotation axis L is 90 °. Is also good. In this case, the four guide grooves 20d are formed at positions where the phase angle about the rotation axis L is 90 °. However, guide grooves 20d may be provided at eight locations that are multiples.

With such a design, the bearing device 1 for this wheel can superimpose the positions of all the hub bolts 40 on all the guide grooves 20d, so that the hub bolts 40 can be easily replaced.

It is assumed that the vertical direction line La intersects the rotation axis L and is parallel to the direction in which gravity acts, and the direction that intersects the rotation axis L and is perpendicular to the vertical direction line is the front-rear direction line Lb. In this case, the guide groove 20d is formed so as not to intersect the front-rear direction line Lb.

With such a design, even if the outer member 2 is deformed so as to expand in the vertical direction, the rigidity of the weir member 20 in the front-rear direction is ensured and the fitting surface pressure of the bearing device 1 for this wheel is secured. Is maintained, so that the weir member 20 can be further prevented from coming off.

Next, the structure applicable to the weir member 20 according to each embodiment will be described with reference to FIG. FIG. 11 corresponds to an enlarged view of the region R in FIG.

In the weir member 20 according to the present embodiment, the outer edge portion of the outer plate portion 20c is bent toward the outer side to cover the gap portion C between the wheel mounting flange 4c and the outer member 2. In the present embodiment, the standing plate portion 20c on the outer side is bent at a predetermined angle, but the bending angle and the bending method are not limited.

With such a design, in the bearing device 1 for this wheel, the standing plate portion 20c on the outer side receives the splashes of muddy water and the floating dust, so that the splashes of muddy water and the floating dust are the sealing member 10 on the other side. Can be prevented from reaching. Therefore, it is possible to further prevent damage to the rolling elements 6 (one-side ball row 6a and the other-side ball row 6b) and improve the bearing life.

Next, the structure applicable to the weir member 20 according to each embodiment will be described with reference to FIG. FIG. 12 corresponds to an enlarged view of the region R in FIG.

In the weir member 20 according to the present embodiment, the outer edge portion of the standing plate portion 20b on the inner side is bent toward the inner side. In the present embodiment, the standing plate portion 20b on the inner side is bent at a predetermined angle, but the bending angle and the bending method are not limited.

With such a design, the bearing device 1 for this wheel has an enhanced effect of blocking muddy water by the standing plate portion 20b on the inner side, so that the muddy water is further transmitted to the outer member 2 to the other side sealing member 10. It can be prevented from reaching.

1 Wheel bearing device 2 Outer member 2c Outer rolling surface 2d Outer rolling surface 3 Inner member 4 Hub wheel 4a Small diameter step 4c Wheel mounting flange 4e Inner rolling surface 5 Inner ring 5a Inner rolling surface 6 Rolling element 6a Ball row 6b Ball row 7 Seal member (one side seal member)
10 Seal member (other side seal member)
20 Weir member 20a Fitting part 20b Standing plate part 20c Standing plate part 20d Guide groove 40 Hub bolt S Circular space C Gap part L Rotation axis La Vertical direction line Lb Front-back direction line Da Gap dimension Db Height dimension of standing plate Height dimension of the plate

Claims (5)

An outer member in which multiple rows of outer rolling surfaces are integrally formed on the inner circumference,
From a hub ring having a wheel mounting flange into which a plurality of hub bolts are press-fitted and having a small-diameter step portion extending in the axial direction formed on the outer circumference, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring. An inner member having a double-row inner rolling surface facing the double-row outer rolling surface formed on the outer circumference thereof.
A double-row rolling element that is rotatably interposed between the rolling surfaces of the outer member and the inner member,
In a wheel bearing device including a seal member internally fitted into the outer member so as to close the outer end of the annular space formed between the outer member and the inner member.
On the outer diameter side of the portion where the seal member is internally fitted, a weir member externally fitted to the outer member is provided.
The weir member has two standing plate portions extending outward in the radial direction, and the standing plate portion on the inner side and the standing plate portion on the outer side are arranged side by side with a predetermined gap .
The plurality of hub bolts are arranged on concentric circles centered on the rotation axis of the inner member in the same phase with each other.
One or both of the standing plate portion on the outer side and the standing plate portion on the inner side is formed with a guide groove for passing the hub bolt.
A vertical line that intersects the rotation axis and is parallel to the direction in which gravity acts,
Similarly, assuming a front-back direction line that intersects the rotation axis and is perpendicular to the vertical direction line,
The guide groove is formed so as not to intersect the front-rear direction line .
Bearing device for wheels. The height dimension of the standing plate portion on the inner side is larger than the height dimension of the standing plate portion on the outer side.
The wheel bearing device according to claim 1. The height dimension of the standing plate portion on the outer side is larger than the height dimension of the standing plate portion on the inner side.
The wheel bearing device according to claim 1. The outer edge of the standing plate on the outer side is bent toward the outer side to cover the gap between the wheel mounting flange and the outer member.
The wheel bearing device according to any one of claims 1 to 3, wherein the wheel bearing device. The guide grooves are formed in the same number or multiples as the hub bolts and in the same phase on the concentric circles.
The wheel bearing device according to any one of claims 1 to 4, wherein the wheel bearing device.

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