JP2018035825A - Bearing device for wheel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device for a wheel which can prevent that muddy water arrives at a seal member along an outer member, hardly causes the come-off of a weir member being a constituent element of this invention even if the deformation of the outer member is repeated, and does not become an obstacle at the exchange of a hub bolt.SOLUTION: A bearing device 1 for a wheel comprises a weir member 20 which is externally fit to an outer member 2 at an outside-diameter side of a portion into which a seal member (the other side seal member 10) is internally fit. The weir member 20 has two erecting plate parts 20b, 20c extending toward the outside of a radial direction, and the inner-side erecting plate part 20b and the outer-side erecting plate part 20c are arranged in parallel with each other with a prescribed interval.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a wheel bearing device.

  2. Description of the Related Art Conventionally, a wheel bearing device that rotatably supports a wheel in a suspension device such as an automobile is known. In the wheel bearing device, an outer member is fixed to a knuckle constituting the suspension device. In the wheel bearing device, an inner member is disposed 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 the wheel attached to the inner member is 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. For this reason, the wheel bearing device is provided with a seal member that seals the annular space in order to prevent the intrusion of muddy water and dust and the leakage of grease. For example, it is 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. And a sealing member that seals the formed annular space. However, in such a wheel bearing device, when the muddy water reaches the seal member through the outer member (see the arrow F shown in FIG. 13A), the seal member is damaged by biting in the foreign matter contained in the muddy water. There was a concern of wear and tear. That is, there is a concern that the sealing performance (durability) of the sealing member is lowered.

  Therefore, the wheel bearing device described in Patent Document 2 includes a weir member that is fitted on the outer member so as to prevent muddy water from reaching the seal member along the outer member. However, in such a wheel bearing device, there is a case where the muddy water may get over the weir member and reach the seal member (see arrow F shown in FIG. 13B), and the seal member may be damaged or worn. There was a problem of not being able to wipe off. That is, there has been a problem that the concern that the sealing performance (durability) of the sealing member is lowered cannot be eliminated.

  In addition, when the vehicle body is turning, it is known that the radial load and the axial load applied to the outer wheel in the turning direction (the left wheel in the case of right turn and the right wheel in the case of left turn) increase. . Then, the outer side end portion of the outer member may be deformed into an elliptical shape, and there has been a problem that the weir member comes off due to repetition of such deformation.

  In addition, the wheel mounting flange of the inner member is provided with a plurality of bolt holes on concentric circles around the rotation axis of the inner member, and hub bolts are press-fitted into the respective bolt holes. 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 the difficulty of getting over muddy water, there is a problem that the hub bolt cannot be replaced because the weir member becomes an obstacle.

JP 2014-219100 A JP 2011-7272 A

  An object of the present invention is to provide a wheel bearing device that can prevent muddy water from reaching the seal member through the outer member. It is another object of the present invention to provide a wheel bearing device in which the weir member, which is a constituent element of the present invention, is not easily removed by repeated deformation of the outer member and does not become an obstacle when the hub bolt is replaced.

  That is, the present invention integrally has an outer member integrally formed with double row outer rolling surfaces on the inner periphery and a wheel mounting flange into which a plurality of hub bolts are press-fitted, and has a small diameter extending in the axial direction on the outer periphery. A hub ring formed with a stepped portion, and at least one inner ring press-fitted into the small-diameter stepped portion of the hub ring, and a double-row inner rolling surface facing the double-row outer rolling surface on the outer periphery. A formed inner member, a double-row rolling element interposed between the rolling surfaces of the outer member and the inner member so as to be freely rollable, the outer member, and the inner member; And a seal member fitted into the outer member so as to close an outer side end portion of the annular space formed between the bearing member and the wheel bearing device. On the outer diameter side, the dam member is fitted on the outer member, and the dam member is radially Has two standing portion extending toward the side, the standing portion of the upright plate portion of the inner side and the outer side is arranged with a predetermined gap, it is intended.

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

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

  In the wheel bearing device according to the present invention, the outer side standing plate portion 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 the concentric circles centering on the rotation axis of the inner member with the same phase, and the outer plate and the inner plate portion One or both of the upright plate portions are formed with guide grooves for allowing the hub bolts to pass therethrough.

  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 phase on the concentric circles.

  In the wheel bearing device according to the present invention, a vertical line that intersects the rotary shaft and is parallel to the direction in which gravity acts, and a longitudinal line that intersects the rotary shaft and is perpendicular to the vertical line And the guide groove is formed so as not to cross the front-rear direction line.

  As effects of the present invention, the following effects can be obtained.

  That is, the wheel bearing device according to the present invention includes a weir member that is fitted on the outer member on the outer diameter side of the portion in which the seal member is fitted. The weir member has two standing plate portions extending radially outward, and the inner side standing plate portion and the outer side standing plate portion are arranged in parallel with a predetermined gap therebetween. Accordingly, in the wheel bearing device, the inner side standing plate portion and the outer side standing plate portion constituting the dam member respectively dam the muddy water, so that the muddy water reaches the seal member along the outer member. Can be prevented. Therefore, the concern that the sealing performance (durability) of the sealing member is reduced can be eliminated, and as a result, the rolling elements can be prevented from being damaged and the bearing life can be improved. Further, since the fitting surface pressure is increased at two locations corresponding to the inner side standing plate portion and the outer side standing plate portion, it is possible to prevent the weir member from coming off.

  In the wheel bearing device according to the present invention, the height of the inner vertical plate is greater than the height of the outer vertical plate. As a result, the bearing device for the present wheel further prevents the weir member from coming off because the fitting surface pressure of the portion corresponding to the upright plate portion on the inner side where the deformation amount of the outer member is relatively small is increased. Can do.

  In the wheel bearing device according to the present invention, the height of the outer standing plate is larger than the height of the inner standing plate. Thereby, the bearing device for the present wheel restrains the outer member to a certain level or more because the fitting surface pressure of the portion corresponding to the outer side standing plate portion where the deformation amount of the outer member is relatively large becomes high. Can be prevented from being deformed.

  In the wheel bearing device according to the present invention, the outer side standing plate portion has its outer edge bent to the outer side to cover the gap portion between the wheel mounting flange and the outer member. Accordingly, in the wheel bearing device according to the present invention, the standing plate on the outer side receives the splash of muddy water and floating sand dust, so that the muddy water splash and floating sand dust can be prevented from reaching the seal member. Therefore, it is possible to further improve the bearing life by preventing the rolling elements from being damaged.

  In the wheel bearing device according to the present invention, the plurality of hub bolts are arranged on the concentric circles centering on the rotation shaft of the inner member with the same phase, and the outer side standing plate portion and the inner side standing plate portion One or both are formed with guide grooves for passing the hub bolts. As a result, the wheel bearing device can replace the hub bolt 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 in the same phase on the concentric circles. Thereby, since this hub bearing device can pile up all the hub bolts in all the guide grooves, it becomes possible to easily replace the hub bolts.

  In the wheel bearing device according to the present invention, an up-down direction line that is parallel to the direction in which the rotation axis intersects with the gravity and a front-rear direction line that intersects the rotation axis and is perpendicular to the up-down direction line, When it is assumed, the guide groove is formed so as not to cross the front-rear direction line. As a result, even if the outer member is deformed so that the outer member expands in the vertical direction, the present wheel bearing device ensures the rigidity of the weir member in the front-rear direction and maintains the fitting surface pressure. Can be prevented from coming off.

The perspective view which shows the whole structure of the wheel bearing apparatus. Sectional drawing which shows the whole structure of the wheel bearing apparatus. The expanded sectional view which shows the partial structure of the wheel bearing apparatus. The expanded sectional view which shows the partial structure of the wheel bearing apparatus. The expanded sectional view showing the dam member concerning a first embodiment. The figure which shows the replacement | exchange operation | work of a hub bolt. The expanded sectional view which shows the dam member which concerns on 2nd embodiment. The figure which shows the replacement | exchange operation | work of a hub bolt. The expanded sectional view showing the dam member concerning a third embodiment. The figure which shows the replacement | exchange operation | work of a hub bolt. The expanded sectional view which shows the dam member which concerns on other embodiment. The expanded sectional view which shows the dam member which concerns on other embodiment. Sectional drawing which shows the partial structure of the conventional wheel bearing apparatus.

  Below, the wheel bearing apparatus 1 which concerns on this invention is demonstrated using FIGS. 1-4. 2 is a cross-sectional view taken along the line AA in FIG. 3 and 4 are enlarged views of a partial region in FIG.

  The wheel bearing device 1 supports a wheel rotatably 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 “other-side seal member 10”). In the following, “one side” represents the vehicle body side of the wheel bearing device 1, that is, the inner side. 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 wheel 4 and inner ring 5). The outer member 2 is made of a medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C formed in a substantially cylindrical shape. An enlarged diameter portion 2 a is formed at the inner side end of the outer member 2. Further, an enlarged diameter portion 2 b is formed at the outer side end portion of the outer member 2. Further, the outer rolling surface 2c and the outer rolling surface 2d are formed in an annular shape on the inner periphery of the outer member 2 so as to be parallel to each other. The outer rolling surface 2c and the outer rolling surface 2d are subjected to induction hardening, and are hardened so that the surface hardness is in the range of 58 to 64 HRC. It should be noted that a knuckle attachment flange 2e for being attached to a knuckle constituting the suspension device is integrally formed on the outer periphery of the outer member 2. Further, a dam member 20 described later is fitted on the outer periphery of the outer member 2.

  The inward member 3 rotatably supports a wheel (not shown). The inner member 3 includes a hub ring 4 and an inner ring 5.

  The hub wheel 4 is made of medium-high carbon steel containing carbon of 0.40 to 0.80 wt% such as S53C formed in a substantially cylindrical shape. A small-diameter step portion 4 a is formed at the inner end of the hub wheel 4. An inner ring 5 is press-fitted into the small diameter step 4a. Further, the small diameter step portion 4a is formed with a caulking portion 4b of the inner ring 5 by bending the inner side end portion radially outward. Further, a wheel mounting flange 4 c is integrally formed on the outer periphery of the hub wheel 4. Bolt holes 4d are provided at equal intervals on a concentric circle centering on the rotation axis L of the inner member 3 in the wheel mounting flange 4c, and hub bolts 40 are press-fitted into the respective bolt holes 4d. In addition, an inner rolling surface 4 e is formed on the outer periphery of the hub wheel 4 in a ring shape. The hub wheel 4 is induction-hardened from the small-diameter step portion 4a through the inner rolling surface 4e to a seal land portion (consisting of a shaft surface portion 4f, a curved surface portion 4g, and a side surface portion 4h described later), and has a surface hardness. It is cured so as to be in the range of 58 to 64 HRC. Thereby, 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 a high carbon chrome bearing steel such as SUJ2 formed in a substantially cylindrical shape. On the outer periphery of the inner ring 5, an inner rolling surface 5a is formed in an annular shape. That is, the inner ring 5 is press-fitted into the small-diameter step portion 4a of the hub wheel 4, and constitutes an inner rolling surface 5a on the outer periphery of the small-diameter step portion 4a. The inner ring 5 is subjected to so-called quenching and is cured so as to be in the range of 58 to 64 HRC up to the core. Thereby, 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 5 a faces the outer rolling surface 2 c of the outer member 2.

  The rolling element 6 is interposed between the outer member 2 and the inner member 3 (hub wheel 4 and inner ring 5). The rolling element 6 has an inner side ball row 6a (hereinafter referred to as “one side ball row 6a”) and an outer side ball row 6b (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 subjected to so-called quenching and are cured so as to be in the range of 58 to 64 HRC up to the core portion. In the one-side ball row 6a, a plurality of balls are held in a ring shape by a cage. The one-side ball row 6a is accommodated so as to be freely rollable between an inner rolling surface 5a formed on the inner ring 5 and an 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 a ring shape by a cage. The other-side ball row 6b is accommodated so as to be freely rollable between an inner rolling surface 4e formed on the hub wheel 4 and an 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 constitute a double-row angular ball bearing with the outer member 2 and the inner member 3 (hub wheel 4 and inner ring 5). The wheel bearing device 1 is a third-generation wheel bearing device in which the inner raceway surface 4e of the other-side ball row 6b is formed on the outer periphery of the hub wheel 4, but is not limited thereto. A second generation structure in which a pair of inner rings 5 are press-fitted and fixed to the hub wheel 4, or a first generation that includes an outer ring that is the outer member 2 and an inner ring that is the inner member 3 without the hub wheel 4. It may be a structure.

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

  The seal ring 8 is fitted (internally fitted) to the enlarged diameter portion 2 a of the outer member 2 and is configured integrally with the outer member 2. The seal ring 8 includes a cored bar 81 and a seal rubber 82 that is an elastic member.

  The cored bar 81 is a ferritic stainless steel plate (JIS standard SUS430 or the like), an austenitic stainless steel plate (JIS standard SUS304 or the like), or a rust-proof cold rolled steel plate (JIS standard SPCC system or the like). It consists of The cored bar 81 is formed by bending an annular steel plate by press work and has an axial cross section that is substantially L-shaped. Thereby, the cored bar 81 is formed with a cylindrical fitting part 81a and a disk-like side plate part 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 perpendicularly, and the fitting portion 81a faces a fitting portion 9a of a slinger 9 described later. Further, the side plate portion 81b faces a side plate portion 9b of the slinger 9 described later. A seal rubber 82, which is an elastic member, is vulcanized and bonded to the fitting portion 81a and the side plate portion 81b.

  The seal rubber 82 is NBR (acrylonitrile-butadiene rubber), HNBR (hydrogenated acrylonitrile-butadiene rubber) excellent in heat resistance, EPDM (ethylene propylene rubber), ACM (polyacrylic rubber) excellent in heat resistance and chemical resistance, It is made of synthetic rubber such as FKM (fluoro 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 periphery of the inner member 3 (the outer periphery of the inner ring 5) and is configured integrally with the inner member 3.

  Slinger 9 is a ferritic stainless steel sheet (JIS standard SUS430 series, etc.), austenitic stainless steel sheet (JIS standard SUS304 series, etc.), or a rust-proof cold rolled steel sheet (JIS standard SPCC system, etc.). It is configured. The slinger 9 is formed by bending an annular steel plate by press working and has an axial cross section formed in a substantially L shape. Thereby, the slinger 9 is formed with a cylindrical fitting portion 9a and a disc-shaped side plate portion 9b extending from the end portion toward the outer member 2. The fitting portion 9a and the side plate portion 9b intersect each other vertically, 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. The side plate portion 9b is provided with a magnetic encoder 9c.

  The one-side seal member 7 is disposed so that the seal ring 8 and the slinger 9 face each other. At this time, the radial lip 82a contacts the fitting portion 9a of the slinger 9 through the oil film. The inner axial lip 82b contacts the side plate portion 9b of the slinger 9 through the oil film. The outer axial lip 82c also contacts the side plate portion 9b of the slinger 9 through the oil film. In this way, the one-side seal member 7 constitutes a so-called pack seal, which prevents intrusion of muddy water and sand dust and prevents leakage of grease.

  The other side sealing 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 includes an annular seal ring 11.

  The other-side seal member 10 is integrally fitted with the outer member 2 by being fitted (internally fitted) to the enlarged diameter portion 2 b of the outer member 2. The seal ring 11 includes a metal core 111 and a seal rubber 112 that is an elastic member.

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

  Seal rubber 112 is NBR (acrylonitrile-butadiene rubber), HNBR (hydrogenated acrylonitrile-butadiene rubber) excellent in heat resistance, EPDM (ethylene propylene rubber), ACM (polyacrylic rubber) excellent in heat resistance and chemical resistance, It is made of synthetic rubber such as FKM (fluoro 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 disposed so that the seal ring 11 and the hub wheel 4 face each other. At this time, the radial lip 112a contacts the shaft surface portion 4f of the hub wheel 4 through the oil film. Further, the axial lip 112b contacts the curved surface portion 4g of the hub wheel 4 through the oil film. The outer axial lip 112c also contacts the side surface portion 4h of the hub wheel 4 through the oil film. In this way, the other-side seal member 10 prevents the intrusion of muddy water and sand dust and 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. 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. FIG. 6 shows the hub bolt 40 replacement operation.

  The weir member 20 according to the first embodiment includes a ferritic stainless steel plate (JIS standard SUS430 series or the like), an austenitic stainless steel sheet (JIS standard SUS304 series or the like), or a rust-proof cold rolled steel plate (JIS standard). Standard SPCC system). The weir member 20 is formed in a substantially U shape in an axial sectional view by bending an annular steel plate by press working. Thereby, the dam 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 portion extending radially outward from the outer side end portion thereof. A plate portion 20c is formed. The fitting portion 20a and the standing plate portion 20b intersect with each other substantially perpendicularly, and the fitting portion 20a and the standing plate portion 20c also intersect with each other substantially perpendicularly. 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 dam member 20 according to the first embodiment, the height dimension Db of the upright plate portion 20b on the inner side is larger than the height size Dc of the upright 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 clearance dimension Da and the height dimension Db ensure at least 5 mm or more.

  By adopting such a design, in the wheel bearing device 1, the inner side standing plate portion 20b and the outer side standing plate portion 20c constituting the weir member 20 respectively dam the muddy water, so that the muddy water is outward. It is possible to prevent the other side sealing member 10 from reaching the member 2. More specifically, a portion of the muddy water transmitted from the inner side standing plate portion 20b is dammed, and the outer side standing plate portion 20c dams the muddy water that has passed over the standing plate portion 20b. It is possible to prevent the other side sealing member 10 from reaching the member 2. Accordingly, the concern that the sealing performance (durability) of the other-side seal member 10 is reduced can be eliminated, and as a result, the rolling elements 6 (the one-side ball row 6a and the other-side ball row 6b) are prevented from being damaged and the bearing life is improved. realizable.

  In addition, since the dam member 20 has the inner side standing plate portion 20b extending 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. Moreover, since the outer side standing plate portion 20c also extends outward in the radial direction, the rigidity at the outer side end portion is high with respect to the load applied in the radial direction. Accordingly, the fitting surface pressure is increased at two locations corresponding to the inner-side standing plate portion 20b and the outer-side standing plate portion 20c (see the surface pressure distribution P), so that the weir member 20 can be prevented from coming off. it can. More specifically, the height Db of the standing plate 20b is larger than the height Dc of the standing plate 20c, so that the fitting surface pressure of the portion corresponding to the standing plate 20c on the outer side is larger. Also, the fitting surface pressure at the portion corresponding to the standing plate portion 20b on the inner side is larger (see the surface pressure distribution P). Then, since the fitting surface pressure of the portion corresponding to the inner side standing plate portion 20b where the deformation amount of the outer member 2 is relatively small is increased, it is possible to further prevent the weir member 20 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 into which the other-side seal member 10 is internally fitted, the weir member 20 can be further prevented 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 weir member 20 has a guide groove 20d of the hub bolt 40 formed on the outer edge portion of the upright plate portion 20b. More specifically, a guide groove 20d for allowing the hub bolt 40 to pass is formed by cutting the outer edge portion of the upright plate portion 20b into an arc shape.

  By adopting such a design, the wheel bearing device 1 can be used with the outer member 2 even if the height dimension Db of the upright plate portion 20b on the inner side is increased in consideration of the difficulty of getting over muddy water. 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 and is provided at positions where the phase angle about the rotation axis L is 72 °. Therefore, five guide grooves 20d in the circumferential direction are formed in the standing plate portion 20b of the dam member 20 at positions where the phase angle about the rotation axis L is 72 °. However, the guide grooves 20d may be provided at ten locations that are multiples. At this time, the guide groove 20d is formed at a position where the phase angle around the rotation axis L is 36 °. The wheel bearing device 1 includes five hub bolts 40. For example, the wheel bearing device 1 includes four hub bolts 40, and is provided at positions where the phase angle about the rotation axis L is 90 °. 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, the guide grooves 20d may be provided at eight locations that are multiples.

  With this design, the wheel bearing device 1 can overlap the positions of all the hub bolts 40 in all the guide grooves 20d, so that the hub bolt 40 can be easily replaced.

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

  By adopting such a design, the present wheel bearing device 1 ensures the rigidity of the weir member 20 in the front-rear direction and the fitting surface pressure even if the outer member 2 is deformed so as to expand in the vertical direction. Therefore, the dam member 20 can be 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. 7A corresponds to an enlarged view of the region R in FIG. 2, and FIG. 7B corresponds to a diagram showing a cross section taken along the line BB in FIG. FIG. 8 shows the replacement work of the hub bolt 40.

  The weir member 20 according to the second embodiment includes 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 rust-proof cold rolled steel plate (JIS standard). Standard SPCC system). The weir member 20 is formed in a substantially U shape in an axial sectional view by bending an annular steel plate by press working. Thereby, the dam 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 portion extending radially outward from the outer side end portion thereof. A plate portion 20c is formed. The fitting portion 20a and the standing plate portion 20b intersect with each other substantially perpendicularly, and the fitting portion 20a and the standing plate portion 20c also intersect with each other substantially perpendicularly. 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 Dc of the outer standing plate 20c is larger than the height Db of the inner standing 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 ensure at least 5 mm.

  By adopting such a design, in the wheel bearing device 1, the inner side standing plate portion 20b and the outer side standing plate portion 20c constituting the weir member 20 respectively dam the muddy water, so that the muddy water is outward. It is possible to prevent the other side sealing member 10 from reaching the member 2. More specifically, a portion of the muddy water transmitted from the inner side standing plate portion 20b is dammed, and the outer side standing plate portion 20c dams the muddy water that has passed over the standing plate portion 20b. It is possible to prevent the other side sealing member 10 from reaching the member 2. Accordingly, the concern that the sealing performance (durability) of the other-side seal member 10 is reduced can be eliminated, and as a result, the rolling elements 6 (the one-side ball row 6a and the other-side ball row 6b) are prevented from being damaged and the bearing life is improved. realizable.

  In addition, since the dam member 20 has the inner side standing plate portion 20b extending 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. Moreover, since the outer side standing plate portion 20c also extends outward in the radial direction, the rigidity at the outer side end portion is high with respect to the load applied in the radial direction. Accordingly, the fitting surface pressure is increased at two locations corresponding to the inner-side standing plate portion 20b and the outer-side standing plate portion 20c (see the surface pressure distribution P), so that the weir member 20 can be prevented from coming off. it can. More specifically, the height dimension Dc of the standing plate portion 20c is larger than the height dimension Db of the standing plate portion 20b, so that the fitting surface pressure of the portion corresponding to the standing plate portion 20b on the inner side is larger. Further, 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, since the fitting surface pressure of the portion corresponding to the outer side standing plate portion 20c where the deformation amount of the outer member 2 is relatively large becomes high, the outer member 2 is restrained to suppress deformation beyond a certain level. Can do. In particular, since the weir member 20 is externally fitted to the outer member 2 on the outer diameter side of the portion in which the other-side seal member 10 is fitted, 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 dam member 20 has a guide groove 20d of the hub bolt 40 formed on the outer edge portion of the upright plate portion 20c. More specifically, a guide groove 20d for allowing the hub bolt 40 to pass is formed by cutting the outer edge portion of the upright plate portion 20c into an arc shape.

  By adopting such a design, the wheel bearing device 1 can be used with the outer member 2 even if the height dimension Dc of the upright plate portion 20c on the outer side is increased in consideration of the difficulty of getting over muddy water. 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 and is provided at positions where the phase angle about the rotation axis L is 72 °. Therefore, five guide grooves 20d in the circumferential direction are formed in the standing plate portion 20c of the dam member 20 at positions where the phase angle about the rotation axis L is 72 °. However, the guide grooves 20d may be provided at ten locations that are multiples. At this time, the guide groove 20d is formed at a position where the phase angle around the rotation axis L is 36 °. The wheel bearing device 1 includes five hub bolts 40. For example, the wheel bearing device 1 includes four hub bolts 40, and is provided at positions where the phase angle about the rotation axis L is 90 °. 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, the guide grooves 20d may be provided at eight locations that are multiples.

  With this design, the wheel bearing device 1 can overlap the positions of all the hub bolts 40 in all the guide grooves 20d, so that the hub bolt 40 can be easily replaced.

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

  By adopting such a design, the present wheel bearing device 1 ensures the rigidity of the weir member 20 in the front-rear direction and the fitting surface pressure even if the outer member 2 is deformed so as to expand in the vertical direction. Therefore, the dam member 20 can be 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. 9A corresponds to an enlarged view of the region R in FIG. 2, and FIG. 9B corresponds to a view showing a cross section taken along the line BB in FIG. FIG. 10 shows the hub bolt 40 replacement operation.

  The weir member 20 according to the third embodiment includes 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 rust-proof cold rolled steel plate (JIS standard). Standard SPCC system). The weir member 20 is formed in a substantially U shape in an axial sectional view by bending an annular steel plate by press working. Thereby, the dam 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 portion extending radially outward from the outer side end portion thereof. A plate portion 20c is formed. The fitting portion 20a and the standing plate portion 20b intersect with each other substantially perpendicularly, and the fitting portion 20a and the standing plate portion 20c also intersect with each other substantially perpendicularly. 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 dam member 20 according to the third embodiment, the inner side standing plate portion 20b and the outer side standing plate portion 20c have the same height dimension Db · Dc (Db = Dc). Further, the gap dimension Da between the standing plate 20b and the standing plate 20c is substantially equal to the height Db of the standing plate 20b and the height Dc of the standing plate 20c (Da≈Db, Dc). The gap dimension Da and the height dimensions Db and Dc are at least 5 mm or more.

  By adopting such a design, in the wheel bearing device 1, the inner side standing plate portion 20b and the outer side standing plate portion 20c constituting the weir member 20 respectively dam the muddy water, so that the muddy water is outward. It is possible to prevent the other side sealing member 10 from reaching the member 2. More specifically, a portion of the muddy water transmitted from the inner side standing plate portion 20b is dammed, and the outer side standing plate portion 20c dams the muddy water that has passed over the standing plate portion 20b. It is possible to prevent the other side sealing member 10 from reaching the member 2. Accordingly, the concern that the sealing performance (durability) of the other-side seal member 10 is reduced can be eliminated, and as a result, the rolling elements 6 (the one-side ball row 6a and the other-side ball row 6b) are prevented from being damaged and the bearing life is improved. realizable.

  In addition, since the dam member 20 has the inner side standing plate portion 20b extending 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. Moreover, since the outer side standing plate portion 20c also extends outward in the radial direction, the rigidity at the outer side end portion is high with respect to the load applied in the radial direction. Accordingly, the fitting surface pressure is increased at two locations corresponding to the inner-side standing plate portion 20b and the outer-side standing plate portion 20c (see the surface pressure distribution P), so that the weir member 20 can be prevented from coming off. it can. More specifically, the fitting surface of the portion corresponding to the inner side standing plate portion 20b due to the height Db of the standing plate portion 20b and the height Dc of the standing plate portion 20c being the same. The fitting surface pressure of the portion corresponding to the pressure and the outer side standing plate portion 20c is the same (see the surface pressure distribution P). Then, since the fitting surface pressure of the portion corresponding to the upright plate portion 20b on the inner side where the deformation amount of the outer member 2 is relatively small is increased, it is possible to further prevent the weir member 20 from being removed, Since the fitting surface pressure of the portion corresponding to the outer side standing plate portion 20c where the deformation amount of the outer member 2 is relatively large is increased, the outer member 2 can be restrained to suppress a certain deformation or more. . In particular, since the weir member 20 is externally fitted to the outer member 2 on the outer diameter side of the portion in which 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 dam member 20 has a guide groove 20d for the hub bolt 40 formed on the outer edge portions of the upright plate portion 20b and the upright plate portion 20c. More specifically, a guide groove 20d for allowing the hub bolt 40 to pass is formed by cutting out the outer edge portions of the upright plate portion 20b and the upright plate portion 20c into an arc shape.

  By adopting such a design, the wheel bearing device 1 takes into account the height dimension Db / Dc of the inner side upright plate portion 20b and the outer side upright plate portion 20c in consideration of the difficulty of getting over muddy water. 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 and is provided at positions where the phase angle about the rotation axis L is 72 °. Therefore, five guide grooves 20d in the circumferential direction are formed in the standing plate portion 20b and the standing plate portion 20c of the dam member 20 at positions where the phase angle about the rotation axis L is 72 °. . However, the guide grooves 20d may be provided at ten locations that are multiples. At this time, the guide groove 20d is formed at a position where the phase angle around the rotation axis L is 36 °. The wheel bearing device 1 includes five hub bolts 40. For example, the wheel bearing device 1 includes four hub bolts 40, and is provided at positions where the phase angle about the rotation axis L is 90 °. 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, the guide grooves 20d may be provided at eight locations that are multiples.

  With this design, the wheel bearing device 1 can overlap the positions of all the hub bolts 40 in all the guide grooves 20d, so that the hub bolt 40 can be easily replaced.

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

  By adopting such a design, the present wheel bearing device 1 ensures the rigidity of the weir member 20 in the front-rear direction and the fitting surface pressure even if the outer member 2 is deformed so as to expand in the vertical direction. Therefore, the dam member 20 can be prevented from coming off.

  Next, the structure applicable to the dam 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 dam member 20 according to the present embodiment, the outer side standing plate portion 20c is bent toward the outer side so as to cover the gap portion C between the wheel mounting flange 4c and the outer member 2. In addition, in this embodiment, although the standing board part 20c on the outer side has a shape bent at a predetermined angle, the bending angle and the manner of bending are not limited.

  By setting it as such a design, since the outer side standing-plate part 20c receives the muddy water splash and the floating sand dust, this wheel bearing apparatus 1 receives the muddy water splash and the floating sand dust on the other side sealing member 10. Can be prevented. Therefore, it is possible to further prevent the rolling elements 6 (the one-side ball row 6a and the other-side ball row 6b) from being damaged and to improve the bearing life.

  Next, the structure applicable to the dam 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 dam member 20 according to the present embodiment, the outer edge portion of the upright plate portion 20b on the inner side is bent toward the inner side. In addition, in this embodiment, although the standing board part 20b by the side of inner side becomes the shape bent by the predetermined | prescribed angle, it does not limit about the bending angle or the aspect of a bending method.

  By adopting such a design, the wheel bearing device 1 increases the muddy water blocking effect by the inner side standing plate portion 20b, so that the muddy water further travels along the outer member 2 to the other side seal member 10. Can be prevented from reaching.

DESCRIPTION OF SYMBOLS 1 Wheel bearing apparatus 2 Outer member 2c Outer rolling surface 2d Outer rolling surface 3 Inner member 4 Hub wheel 4a Small diameter step part 4c Wheel mounting flange 4e Inner rolling surface 5 Inner ring 5a Inner rolling surface 6 Rolling body 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 portion 20b Standing plate portion 20c Standing plate portion 20d Guide groove 40 Hub bolt S Annular space C Clearance portion L Rotating shaft La Vertical line Lb Front-rear direction line Da Clearance dimension Db Standing plate height dimension Dc Standing Plate height

Claims (7)

An outer member in which a double row outer rolling surface is integrally formed on the inner periphery;
A hub wheel integrally having a wheel mounting flange into which a plurality of hub bolts are press-fitted and formed with a small-diameter step portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring An inner member in which a double row inner rolling surface facing the outer rolling surface of the double row is formed on the outer periphery,
A double-row rolling element interposed between the rolling surfaces of the outer member and the inner member so as to freely roll;
In a wheel bearing device comprising: a seal member fitted into the outer member so as to close an outer side end portion of an annular space formed between the outer member and the inner member,
On the outer diameter side of the portion in which the seal member is fitted, a dam member fitted to the outer member is provided,
The dam 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 in parallel with a predetermined gap therebetween. A wheel bearing device characterized by the above.   2. The wheel bearing device according to claim 1, wherein a height dimension of the upright plate portion on the inner side is larger than a height size of the upright plate portion on the outer side.   2. The wheel bearing device according to claim 1, wherein a height dimension of the standing plate portion on the outer side is larger than a height dimension of the standing plate portion on the inner side.   4. The outer standing side plate portion of the outer side is bent toward the outer side to cover a gap portion between the wheel mounting flange and the outer member. A wheel bearing device according to claim 1.   The plurality of hub bolts are disposed on concentric circles centering on the rotation axis of the inner member in the same phase, and one or both of the upright plate portion on the outer side and the upright plate portion on the inner side are The wheel bearing device according to any one of claims 1 to 4, wherein a guide groove for passing a hub bolt is formed.   6. The wheel bearing device according to claim 5, wherein the guide grooves are formed in the same number or multiples as the hub bolts and in the same phase on the concentric circles. An up-down direction line that intersects the rotation axis and is parallel to the direction in which gravity acts;
Similarly, assuming a front-rear direction line that intersects the rotation axis and is perpendicular to the up-down direction line,
The wheel bearing device according to claim 5 or 6, wherein the guide groove is formed so as not to intersect the front-rear direction line.

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