JP2019128018A - Wheel bearing device - Google Patents

Abstract

To provide a wheel bearing device which can maintain sealability.SOLUTION: A wheel bearing device 1 includes an inner side seal member 6 which seals a space between an outer ring 2 and an inner ring 4. The inner side seal member 6 has: a seal plate 7 fitted in the outer ring 2; and a slinger 10 including a cylindrical part 10a fitted in the inner ring 4 and a standing plate part 10b extending from the cylindrical part 10a to the radial outer side. The seal plate 7 includes a third side lip d provided closer to the radial outer side than the standing plate part 10b. The third side lip 9d is pressed to the slinger 10 by external force generated by water pressure.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 provided in a vehicle chassis or the like, and an inner member including a hub ring is rotatably supported via a rotating body. The wheel bearing device is provided with a seal member that closes a gap between the outer member and the inner member. The seal member on the inner side (vehicle side) is a combination of a seal plate fitted to the outer member of the wheel bearing device and a slinger fitted to the inner member so as to cover the seal plate. It is configured as a pack seal. A plurality of seal lips provided on the seal plate contact the slinger to prevent the leakage of grease inside and prevent the intrusion of rain water, muddy water, dust and the like from the outside by the seal member provided on the seal plate being in contact with the slinger.

  Among such wheel bearing devices, in order to obtain a long bearing life even under a severe use environment exposed to dust or muddy water, some seal members are provided with a plurality of seal lips to improve sealability. . For example, there is one that constitutes a labyrinth and suppresses dust or muddy water from entering the pack seal. With such a configuration, the pack seal can suppress entry of dust or muddy water to the tip of the seal lip by the labyrinth, can prevent damage to the tip of the seal lip, and can improve sealing performance. For example, as described in Patent Document 1.

  The seal member described in Patent Document 1 has a cylindrical portion extending from the outer peripheral portion of the slinger toward the seal plate. In the seal member, a labyrinth is constituted by a slight gap between the outer peripheral surface of the cylindrical portion and the seal plate. In the seal member, the seal plate is provided with a plurality of seal lips and is in contact with the slinger. Thus, the seal member suppresses the inflow of dust or mud by the labyrinth seal and blocks the dust or mud entering inside by the seal lip.

JP, 2016-211595, A

  However, when the vehicle is traveling in rainy weather or when traveling on a road surface in which muddy water is immersed, the height of the water surface may reach the position of the seal member of the wheel bearing device. At this time, external force due to water pressure is applied to the seal member, and mud water or the like may pass through the labyrinth seal and enter the seal lip. If muddy water or the like gets in between the seal lip and the slinger, the seal lip or the slinger may be damaged and the sealability may be reduced.

  The present invention has been made in view of the above situation, and an object of the present invention is to provide a wheel bearing device capable of maintaining the sealing performance even when an external force due to water pressure is applied to the sealing member.

  That is, the first invention is press-fitted into an outer member having a double row outer raceway surface on the inner periphery, a hub wheel having a small diameter step portion extending in the axial direction on the outer periphery, and the small diameter step portion. An inner member having at least one inner ring and provided on the outer periphery with a double-row inner raceway surface facing the double-row outer raceway surface, and the respective raceways of the outer member and the inner member In a wheel bearing device comprising: a double row rolling element housed so as to roll between surfaces; and a seal member that seals between the outer member and the inner member, the seal member includes: A seal plate fitted to the outer member; a slinger including a cylindrical portion fitted to the inner member; and a standing plate portion extending radially outward from the cylindrical portion; A seal lip provided radially outward from the standing plate portion, and the seal lip is It is pressed against the slinger by an external force.

  According to a second aspect of the invention, the slinger further includes a collar portion extending from the upright plate portion toward the seal plate, and the seal lip is pressed against the collar portion by an external force.

  According to a third aspect of the invention, the tip end of the seal lip is pressed against the standing plate portion by an external force.

  In a fourth aspect of the invention, a labyrinth gap is formed between the seal lip and the outer peripheral surface of the slinger.

  The effects of the present invention are as follows.

  That is, according to the first and third inventions, since the seal lip is pressed against the slinger by the external force, the contact surface pressure between the seal lip and the slinger is increased, and between the seal lip and the sliding surface of the slinger. Intrusion of muddy water into the water is suppressed. Thereby, even if an external force due to water pressure is applied to the sealing member, the sealing performance can be maintained.

  According to the second invention, the seal lip is pressed against the buttocks by the external force, so the contact surface pressure and the contact area between the seal lip and the slinger increase according to the magnitude of the external force, and the slide of the seal lip and the slinger Intrusion of muddy water and the like between the surfaces is suppressed. Thereby, even if an external force due to water pressure is applied to the sealing member, the sealing performance can be maintained.

  According to the fourth invention, when no external force is applied, the seal lip and the slinger constitute a non-contact type labyrinth seal to suppress the rotational torque, and when the external force due to water pressure is applied, the seal lip and the slinger Constitutes a contact-type seal and exhibits high sealing performance. Thereby, even if an external force due to water pressure is applied to the sealing member, the sealing performance can be maintained.

The perspective view which shows the whole structure in one Embodiment of the wheel bearing apparatus. Sectional drawing which shows the whole structure in one Embodiment of the bearing apparatus for wheels. The partially expanded step surface view which shows the structure of a seal member in 1st embodiment of a seal member. The partially expanded step surface view which shows the detailed structure of a sealing member in 1st embodiment of a sealing member. The partially expanded step view which shows the state of the seal member when external force is added in 1st embodiment of a seal member. FIG. 7 is a partially enlarged step view showing a state of the seal member in the case where an external force larger than that in the state of FIG. The partially expanded step surface view which shows the state of the seal member when external force is added in 2nd embodiment of a seal member.

  Below, the wheel bearing apparatus 1 which is 1st embodiment of the wheel bearing apparatus which concerns on this invention using FIGS. 1-3 is demonstrated.

  As shown in FIGS. 1 and 2, the wheel bearing device 1 rotatably supports wheels in a suspension system of a vehicle such as a car. The wheel bearing device 1 includes an outer ring 2 that is an outer member, a hub ring 3 that is an inner member, an inner ring 4, two rows of inner side tapered rollers 5a that are rolling rows, an outer side tapered roller 5b, and a seal member. The inner side seal member 6 according to the first embodiment and the outer side seal member 11 as the seal member are provided. The inner side seal member 6 and the outer side seal member 11 are wheel bearing seals. In this specification, the inner side refers to the vehicle side of the wheel bearing device 1 when the wheel bearing device 1 is attached to the vehicle body, and the outer side refers to the wheel bearing device 1 attached to the vehicle body. The wheel side of the wheel bearing apparatus 1 is represented. Further, a direction parallel to the rotation axis of the wheel bearing device 1 is “axial direction”, a direction orthogonal to the rotation axis of the wheel bearing device 1 is “radial direction”, and the rotation axis of the wheel bearing device 1 is the center. The direction along the arc is represented as “circumferential direction”.

  As shown in FIG. 2, the outer ring 2 supports the hub ring 3 and the inner ring 4. The outer ring 2 is formed in a substantially cylindrical shape. At the inner side end of the outer ring 2, an inner side opening 2a to which the inner side seal member 6 can be fitted is formed. An outer side opening 2 b into which the outer side seal member 11 can be fitted is formed at the outer side end of the outer ring 2.

  On the inner peripheral surface of the outer ring 2, an inner side outer raceway surface 2c and an outer side outer raceway surface 2d are provided. The outer raceway surfaces 2c and 2d are formed in a tapered shape having an inner diameter that increases in a direction away from each other in the axial direction. On the outer peripheral surface of the outer ring 2, a vehicle body attachment flange 2 e for attaching to a knuckle of a suspension device (not shown) is integrally formed.

  The hub wheel 3 rotatably supports wheels of a vehicle (not shown). The hub wheel 3 is formed in a bottomed cylindrical shape. At the inner side end of the hub wheel 3, a small diameter step 3a whose diameter is reduced on the outer peripheral surface is formed. At the outer end of the hub wheel 3, a wheel mounting flange 3b for mounting the wheel is integrally formed. The hub bolt 3d is inserted through the wheel mounting flange 3b at circumferentially equidistant positions. Further, the hub wheel 3 is disposed such that the inner side raceway surface 3 c on the outer side faces the outer side raceway surface 2 d of the outer ring 2. The inner raceway surface 3c on the outer side is formed in a tapered shape whose outer diameter increases toward the outer side. A large collar portion for guiding the outer tapered roller 5b is formed on the large diameter side of the inner raceway surface 3c, and a small collar portion for preventing the outer tapered roller 5b from falling off is formed on the small diameter side. It is done. The inner circumference of the hub wheel 3 is formed with serrations (or splines) for torque transmission. In the hub wheel 3, the inner ring 4 is fitted in the small diameter step 3 a.

  The inner ring 4 applies a preload to the inner tapered roller 5a and the outer tapered roller 5b. An annular inner raceway surface 4 a is formed on the outer peripheral surface of the inner ring 4 in the circumferential direction. The inner raceway surface 4a is formed in a tapered shape in which the outer diameter increases toward the inner side. A large collar portion for guiding the inner side tapered roller 5a is formed on the large diameter side of the inner raceway surface 4a, and a small collar portion for preventing the inner side tapered roller 5a from falling off is formed on the small diameter side. It is done. The inner ring 4 is fixed to the hub wheel 3 by rocking and caulking the inner end of the hub wheel 3. That is, the inner raceway 4 a is formed by the inner ring 4 on the inner side of the hub ring 3. The hub wheel 3 is disposed such that the inner raceway surface 4a of the inner ring 4 at the inner side end faces the outer race 2 outer raceway surface 2c.

  The inner side tapered rollers 5a and the outer side tapered rollers 5b, which are rolling rows, rotatably support the hub wheel 3. The inner side tapered roller 5 a and the outer side tapered roller 5 b are held by a cage 16. The inner tapered roller 5 a is rollably interposed between the inner raceway surface 4 a of the inner ring 4 and the outer raceway surface 2 c of the outer ring 2. The outer side tapered roller 5b is sandwiched between the inner raceway surface 3c of the hub wheel 3 and the outer raceway surface 2d of the outer ring 2 so as to be freely rollable. In the wheel bearing device 1, a double-row tapered roller bearing is constituted by an outer ring 2, a hub ring 3, an inner ring 4, an inner side tapered roller 5a, and an outer side tapered roller 5b.

  As shown in FIGS. 2 and 3, the inner side sealing member 6, which is the first embodiment of the sealing member according to the present invention, closes the gap between the inner side opening 2 a of the outer ring 2 and the inner ring 4. . The inner side seal member 6 is constituted by a two-side lip type seal that contacts two side lips, and a substantially cylindrical seal plate 7 and a substantially cylindrical slinger 10 constitute a pack seal. In addition, in the following embodiment, the inner side sealing member 6 should just be a pack seal provided with a single or several seal lip.

  The seal plate 7 is fitted in the inner opening 2 a of the outer ring 2. The seal plate 7 is composed of a cored bar 8 and a rubber member 9 (see the thin ink portion). The core metal 8 is, for example, a ferritic stainless steel plate (SUS430 series etc. according to JIS standard), an austenitic stainless steel plate (SUS304 series etc. according to JIS standard), or a cold-rolled steel plate subjected to rustproofing treatment (SPCC series according to JIS standard) Etc.). The cored bar 8 is formed in a substantially L-shape in an axial sectional view. Thereby, the metal core 8 includes a cylindrical seal plate fitting portion 8a and an annular support portion 8b extending radially inward from the seal plate fitting portion 8a (the outer side end portion thereof). It is done.

  A rubber member 9 is vulcanized and bonded to the inner side end of the seal plate fitting portion 8a. The rubber member 9 includes a seal lip base portion 9e vulcanized and bonded to the core metal 8, and a radial lip 9a, a first side lip 9b, a second side lip 9c, and a third side lip 9d extending from the seal lip base portion 9e. A sealing lip. The rubber member 9 is made of, for example, NBR (acrylonitrile-butadiene rubber), HNBR (hydrogenated acrylonitrile butadiene rubber) excellent in heat resistance, EPDM (ethylene propylene rubber), ACM (polyacrylic acid excellent in heat resistance and chemical resistance) Rubber), FKM (fluoro rubber), or synthetic rubber such as silicon rubber.

  The slinger 10 is disposed closer to the inner side than the seal plate 7. The slinger 10 is made of, for example, a steel plate of the same material as the seal plate 7. The slinger 10 is formed in a substantially U-shape in an axial cross-sectional view. Thus, the slinger 10 has a cylindrical portion 10a, an annular upright plate portion 10b extending radially outward from the inner side end of the cylindrical portion 10a, and an outer peripheral portion of the upright plate portion 10b toward the seal plate 7. It is comprised from the cylindrical collar part 10c extended. The cylindrical portion 10 a extends in the axial direction and is fitted to the inner ring 4. The upright plate portion 10 b faces the support portion 8 b of the core metal 8 in the axial direction. The flange portion 10c is disposed between the second side lip 9c and the third side lip 9d, and extends horizontally in the axial direction. Further, the flange portion 10c has a minute gap between the axial outer side end and the support portion 8b. Thereby, the collar part 10c comprises the labyrinth seal between the support parts 8b.

  The radial lip 9a is in contact with the outer peripheral surface of the cylindrical portion 10a via an oil film, and mainly prevents leakage of grease sealed inside the wheel bearing device 1 to the outside. The first side lip 9b is in contact with the outer side surface of the upright plate portion 10b via an oil film, and mainly prevents dust and the like from entering the wheel bearing device 1 from the outside. Further, the second side lip 9c is in contact with the upright plate portion 10b via the oil film on the radially outer side of the first side lip 9b, and prevents muddy water etc. from entering the wheel bearing device 1 mainly from outside. There is.

  The third side lip 9d is disposed radially outward of the second side lip 9c and the flange portion 10c. The third side lip 9 d is formed to overlap with the collar 10 c in a radial direction. The radially outer surface of the third side lip 9d is formed as an inclined surface that faces radially inward from the outer side toward the inner side. Further, the third side lip 9d is configured with a labyrinth of a minute gap between its radially inner side surface and the flange portion 10c. That is, the 3rd side lip 9d and the collar part 10c are comprised as the labyrinth seal La, and mainly prevent the penetration | invasion of muddy water from the exterior of the wheel bearing apparatus 1 into the inside.

  As shown in FIG. 2, the outer seal member 11 closes the gap between the outer opening 2 b of the outer ring 2 and the hub wheel 3. The outer seal member 11 is configured as an integral seal in which a seal lip 13 is bonded to, for example, a substantially cylindrical core metal 12 by vulcanization.

  The core metal 12 of the outer side sealing member 11 is, for example, a ferritic stainless steel plate (SUS430 series etc. according to JIS standard), an austenitic stainless steel plate (SUS304 series etc. according to JIS standard), or a cold rolled steel plate subjected to rustproofing (JIS standard SPCC system, etc.). The core metal 12 is formed in a substantially L shape in an axial cross-sectional view by bending an outer edge portion of an annular steel plate by press working. The seal lip 13 is made of, for example, NBR (acrylonitrile-butadiene rubber), HNBR (hydrogenated acrylonitrile butadiene rubber) excellent in heat resistance, EPDM (ethylene propylene rubber), ACM (polyacrylic acid excellent in heat resistance and chemical resistance) Rubber), FKM (fluoro rubber), or synthetic rubber such as silicon rubber.

  The core metal 12 is fitted into the outer opening 2 b of the outer ring 2. At this time, the outer seal member 11 is disposed such that the seal lip 13 is in contact with the seal sliding surface of the hub wheel 3. The outer seal member 11 is configured to be slidable with respect to the seal sliding surface by the seal lip 13 coming into contact with the seal sliding surface of the hub wheel 3 via the oil film.

  In the wheel bearing device 1 configured as described above, the hub wheel 3 and the inner ring 4 are rotatably supported by the outer ring 2 via the inner tapered roller 5a and the outer tapered roller 5b. In the wheel bearing device 1, the gap between the inner side opening 2 a of the outer ring 2 and the inner ring 4 is closed by the inner side seal member 6, and the gap between the outer side opening 2 b of the outer ring 2 and the hub ring 3 is closed. The outer seal member 11 is closed. Thus, in the wheel bearing device 1, the hub ring 3 and the inner ring 4 supported by the outer ring 2 rotate while preventing leakage of lubricating grease from the inside and entry of rainwater or dust from the outside.

  Next, the sealing state of the third side lip 9 d and the flange portion 10 c of the slinger 10 will be described in detail with reference to FIGS. 4 to 6.

  As shown in FIG. 4, the labyrinth seal La which consists of the labyrinth clearance gap G of a predetermined | prescribed magnitude | size is comprised between the 3rd side lip 9d and the collar part 10c. The labyrinth gap G is smaller than the gap between the third side lip 9 d and (the inner peripheral surface 9 f of) the seal lip base 9 e. The third side lip 9d formed of an elastic material such as NBR is formed to bend radially inward based on a predetermined spring constant.

  The inner peripheral surface of the third side lip 9d is inclined so as to approach the flange portion 10c from the proximal end toward the distal end. Further, the outer peripheral surface of the third side lip 9d is inclined so as to be separated from the inner peripheral surface 9f of the seal lip base 9e from the base toward the tip. The thickness of the third side lip 9 d decreases from its base to its tip. The third side lip 9d bends toward the buttocks 10c according to the size thereof when an external force due to water pressure is applied. As a result, the size of the labyrinth gap G between the third side lip 9d and the collar portion 10c fluctuates according to the size of the external force applied to the third side lip 9d.

  When external force, for example, water pressure Pw, is not applied to the third side lip 9d, the third side lip 9d constitutes a labyrinth seal La between the flange portion 10c. The wheel bearing device 1 maintains the sealing performance while suppressing the rotational torque by the labyrinth gap G between the third side lip 9 d and the collar portion 10 c.

  As shown in FIG. 5, when the water pressure Pw such as mud Mu is added to the third side lip 9 d (refer to the solid-painted arrow), the third side lip 9 d becomes more flexible as the water pressure Pw increases, and the labyrinth gap G Becomes smaller. That is, the third side lip 9d is a labyrinth between the ridge 10c and the water pressure Pw, which is a force by which the muddy water Mu or the like tries to enter between the outer peripheral surface of the third side lip 9d and the seal lip base 9e. The gap G is reduced, and the sealing performance as the labyrinth seal La is enhanced.

  As shown in FIG. 6, when the reference water pressure P0 within the range of the water pressure Pw that can prevent the mud mud from entering with the labyrinth seal La is reached (see the black arrow), the third side lip 9d has its tip A part contacts the collar part 10c. As a result, the third side lip 9d acts as a contact seal of the labyrinth gap G = 0 with higher sealing performance from the non-contact labyrinth seal La. In the third side lip 9d, the surface pressure in the region E and the region E that are in contact with the flange portion 10c increases as the water pressure Pw increases. That is, in the third side lip 9d, as the water pressure Pw increases, the sealing performance is further improved by the larger area E contacting the flange portion 10c with a higher surface pressure.

  In the wheel bearing device 1 configured as described above, when no external force is applied, the third side lip 9d configures the labyrinth seal La to suppress the rotational torque while maintaining the sealing performance. When the water pressure Pw is applied, the seal structure of the third side lip 9d changes from the non-contact labyrinth seal La to the contact seal according to the magnitude of the water pressure Pw. Thereby, in the inner side sealing member 6, it is possible to block the entry of the mud Mu into the space on the inner diameter side of the third side lip 9d. Furthermore, in the wheel bearing device 1, the size of the region E in contact with the flange portion 10c of the third side lip 9d constituting the contact-type seal and the surface pressure thereof are determined according to the size of the water pressure Pw. Change. As a result, the wheel bearing device 1 maintains the sealing performance of the inner seal member 6 even if external force due to the water pressure Pw is applied to the inner seal member 6 and the force of mud fluid etc. entering the seal increases. it can. In the present embodiment, the third side lip 9d constitutes a labyrinth seal La that is not in contact with the slinger 10 when no external force is applied, so that the wheel bearing device 1 at the time of no external pressure is applied. In the state where no external force is applied, a contact type seal in contact with the slinger 10 may be configured.

  Next, the inner side sealing member 14 which is 2nd embodiment of the sealing member which concerns on this invention is demonstrated using FIG. In addition, the inner side seal member 14 according to the following embodiment is applied in place of the inner side seal member 6 in the inner side seal member 6 shown in FIGS. The same reference numerals are used to indicate the same components, and in the following embodiments, the same points as those of the embodiments already described will be omitted, and the differences will be mainly described. .

  As shown in FIG. 7, the wheel bearing device 1 includes an inner side seal member 14 that is a seal member. The inner side seal member 14 comprises a substantially cylindrical seal plate 7 and a substantially cylindrical slinger 15 having a weir.

  The seal plate 7 is composed of a core metal 8 and a rubber member 9. A radial lip 9a, a first side lip 9b, a second side lip lip 9c, and a third side lip 9d are integrally formed in this order on the one side (inner side) surface of the support portion 8b of the cored bar 8 from the radially inner side. For example, vulcanized and bonded.

  The slinger 15 is made of, for example, a steel plate equivalent to the seal plate 7. The slinger 15 is formed in a substantially L shape in an axial cross-sectional view by bending an inner edge portion of an annular steel plate by pressing. Thus, the slinger 15 is composed of a cylindrical portion 15a and an annular standing plate portion 15b extending radially outward from the inner side end of the cylindrical portion 15a. The slinger 15 is disposed on the inner side of the seal plate 7, and the cylindrical portion 15 a is fitted and fixed to the inner ring 4. The standing plate portion 15 b is disposed to axially face the support portion 8 b of the core metal 8 constituting the seal plate 7 to constitute a pack seal.

  The tip of the third side lip 9d of the rubber member 9 constituting the seal plate 7 is disposed radially outside the radially outer end face of the standing plate portion 15b of the slinger 10. The tip of the third side lip 9 d is formed so as to overlap with the radially outer end surface of the upstanding plate portion 15 b in the radial direction. That is, the third side lip 9 d is formed so as to cover the space between the support portion 8 b of the core metal 8 constituting the seal plate 7 and the upright plate portion 15 b. The third side lip 9d has a labyrinth with a minute gap between its radially inner side surface and the radially outer end surface of the upright plate portion 15b. That is, the third side lip 9d and the radially outer end surface of the upright plate portion 15b are configured as a labyrinth seal La, and mainly prevent mud etc. from entering the inside of the wheel bearing device 1. As a result, the inner side seal member 14 is configured such that the seal lip is slidable with respect to the slinger 10, and leakage of lubricating grease from the inner side opening 2a of the outer ring 2 and entry of rainwater or dust from the outside are allowed. To prevent.

  A labyrinth seal La including a labyrinth gap G having a predetermined size is formed between the third side lip 9d and the radially outer end surface of the standing plate portion 15b of the slinger 10. The third side lip 9d formed of an elastic body such as NBR is a vertical plate disposed on the radially inner side of the third side lip 9d when a water pressure Pw such as mud mu is applied (see a black arrow). Flex toward the radially outer end face of the portion 15 b (see two-dot chain line). As a result, the size of the labyrinth gap G between the third side lip 9d and the radially outer end face of the standing plate portion 15b fluctuates according to the size of the external force.

  In the wheel bearing device 1, when no external force is applied to the inner side seal member 14, the third side lip 9 d constitutes the labyrinth seal La and suppresses the rotational torque while maintaining the sealing performance. When the water pressure Pw is applied as an external force to the inner side seal member 14, the wheel bearing device 1 causes the third side lip 9d to bend toward the radially outer end face of the upright plate portion 15b (see the two-dot chain line). The size of the labyrinth gap G varies according to the size of the water pressure Pw, and the third side lip 9d changes to a contact-type seal that contacts the radially outer end surface of the upright plate portion 15b. Further, the area pressure of the third side lip 9d changes with the area E in contact with the radially outer end face of the upright plate portion 15b.

  The wheel bearing device 1 configured as described above can maintain the sealing performance even when an external force due to the water pressure Pw is applied to the inner side seal member 14 and the force of entering muddy water increases.

  In the present embodiment, when an external force due to the water pressure Pw is applied, the tip of the third side lip 9d is pressed against the flange portion 10c that extends horizontally in the axial direction, but this is not restrictive. For example, the third side lip is inclined to the inner peripheral surface 9f of the seal lip base portion 9e as it goes from the inner side to the outer side and extends in parallel with the inner peripheral surface of the third side lip 9d. The entirety of 9d may be pressed. Moreover, although the wheel bearing device 1 which is 1st embodiment of a wheel bearing device is comprised from the double row tapered roller bearing, it may comprise also the wheel bearing device which is bearings, such as a double row angular ball bearing. Good.

  Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments in any way, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is shown by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including. Moreover, in the present embodiment, the wheel bearing device 1 is configured as the wheel bearing device 1 of the third generation structure in which the inner raceway surface 3 c is directly formed on the outer periphery of the hub wheel 3, but is limited to this. 2nd generation structure in which a pair of inner rings 4 are press-fitted and fixed to the hub ring 3, or a double-row angular ball bearing or a double-row tapered roller bearing between the knuckle and the hub ring constituting the suspension device. It may be a first generation structure in which the wheel bearing is fitted. In the case of the wheel bearing device of the first generation structure or the second generation structure, the seal member according to the above-described embodiment may be adopted not only for the inner side seal member but also for the outer side seal member.

1 wheel bearing device 2 outer ring 3 hub wheel 4 inner ring 5a inner side tapered roller 5b outer side tapered roller 6 inner side seal member 7 seal plate 9d seal lip (third side lip)
10 Slinger 10a Cylindrical part 10b Standing plate part 10c Gutter part

Claims (4)

An outer member provided with a double-row outer raceway surface on the inner periphery;
A double-row inner race having a hub wheel having a small diameter step extending in the axial direction on the outer periphery, and at least one inner ring press-fit into the small diameter step, and facing the outer raceway surface of the double row on the outer periphery An inner member provided with a surface;
A double row rolling element housed movably between the raceway surfaces of the outer member and the inner member;
A seal member that seals between the outer member and the inner member;
In a wheel bearing device comprising:
The seal member includes a seal plate fitted to the outer member, a slinger including a cylindrical portion fitted to the inner member, and an upright plate portion extending radially outward from the cylindrical portion. ,
The seal plate includes a seal lip provided on a radially outer side than the standing plate portion,
The bearing device for a wheel, wherein the seal lip is pressed against the slinger by an external force. The slinger further includes a flange portion extending from the standing plate portion toward the seal plate,
The wheel bearing device according to claim 1, wherein the seal lip is pressed against the flange by an external force.   The wheel bearing device according to claim 1, wherein a tip end of the seal lip is pressed against the standing plate portion by an external force.   The wheel bearing device according to any one of claims 1 to 3, wherein a labyrinth gap is formed between the seal lip and the outer peripheral surface of the slinger.

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