JP2013044420A - Wheel bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a wheel bearing device with constituent components having added values for improving sealing performance without need of arranging a seal with high sealing performance.SOLUTION: A slinger 14 comprises a cylindrical part 14a to which an inner race 5 is externally fitted and a vertical plate 14b extending outward in a radial direction. A seal plate 15 comprises a core metal 17 internally fitted to the end of an outer member 2, and a seal member 18 with a side lip 18a integrally adhered to this by vulcanized adhesion, extending outward in the radial direction at a slant, and slidingly contacting the vertical plate 14b. The seal member 18 is equipped with an elastic fitting part 18d going around and joined to the end of the core metal 17, and crimped to the outer member 2. The seal plate 15 and the outer edge of the vertical plate 14b face each other through a slight clearance in the radial direction, composing a labyrinth seal 19. A magnetic encoder 16 is integrally adhered by vulcanized adhesion in the side face of the vertical plate 14b, and in the corner of this outer diameter part, a cut-in groove 20 slanting in the outer diameter side is formed.

Description

  The present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like with respect to a suspension device, and in particular, a pulser ring that forms a rotational speed detection device in a pair with a rotational speed sensor that detects the rotational speed of the wheel. The present invention relates to a built-in wheel bearing device.

  In order to rotatably support the wheel of the automobile with respect to the suspension device and to control the anti-lock brake system (ABS), the rotational speed detection device is configured in combination with a rotational speed sensor that detects the rotational speed of the wheel. 2. Description of the Related Art Conventionally, wheel bearing devices having a built-in pulsar ring have various structures. An example of this conventional wheel bearing device is shown in FIG.

  This wheel bearing device is supported and fixed to a suspension device (not shown), and an outer member 51 serving as a fixing member, and an inner member 52 inserted into the outer member 51 via double rows of balls 53 and 53. And have. In the following description, the side closer to the outer side of the vehicle in a state assembled to the vehicle is referred to as an outer side (left side in FIG. 8), and the side closer to the center is referred to as an inner side (right side in FIG.

  The outer member 51 integrally has a vehicle body mounting flange 51b to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and double row outer rolling surfaces 51a, 51a are integrated on the inner periphery. Is formed.

  The inner member 52 has double-row inner rolling surfaces 55a and 56a facing the outer rolling surfaces 51a and 51a of the outer member 51 described above on the outer periphery. Of these double-row inner rolling surfaces 55 a and 56 a, the outer inner rolling surface 55 a is integrally formed on the outer periphery of the hub wheel 55, and the inner inner rolling surface 56 a is formed on the outer periphery of the inner ring 56. . The inner ring 56 is press-fitted into a cylindrical small-diameter step portion 55b extending in the axial direction from the inner rolling surface 55a of the hub wheel 55. The double-row balls 53 and 53 are respectively accommodated between the rolling surfaces and are held by the cages 57 and 57 so as to be freely rollable.

  The hub wheel 55 integrally has a wheel mounting flange 54 for mounting a wheel (not shown) on the outer periphery, and a crimped portion 58 is formed by plastically deforming an end portion of the small diameter step portion 55b radially outward. Has been. The inner ring 56 is fixed in the axial direction by the caulking portion 58. The inner member 52 refers to the hub ring 55 and the inner ring 56. Seals 59 and 60 are attached to both ends of the outer member 51, and a cap 61 is attached to cover the opening on the inner side of the outer member 51. The seals 59, 60 and the cap 61 prevent leakage of grease sealed inside the bearing and intrusion of rainwater, dust, and the like from the outside into the bearing.

  The cap 61 attached to the outer member 51 includes a cored bar 62 formed by pressing a corrosion-resistant steel plate and a bottomed cup-shaped cap main body 63 molded integrally with the cored bar 62. Become. The cap body 63 is formed by injection molding from a synthetic resin material, and is filled with a fibrous reinforcing material made of GF (glass fiber).

  A pulsar ring 64 is disposed on the inner side of the seal 60. The pulsar ring 64 has a substantially L-shaped cross section formed by pressing from a ferromagnetic steel plate, and is bent inward in the radial direction from a cylindrical portion 65a that is press-fitted into the inner ring 56 and the end of the cylindrical portion 65a. A support ring 65 composed of the upright plate portion 65 b and an encoder 66 joined to the support ring 65 are provided.

  The encoder 66 is made of rubber or other elastomer mixed with magnetic powder such as ferrite, and is integrally joined to the inner side surface of the standing plate portion 65b of the support ring 65 by vulcanization adhesion or the like. The encoder 66 is composed of a rubber magnet having magnetic poles N and S alternately magnetized in the circumferential direction, constitutes a magnetic rotary encoder for detecting the rotational speed of the wheel, and has a predetermined axis for the rotational speed sensor (not shown). It faces through a directional clearance (air gap).

  Here, a plurality of pleated fins 67 project from the cylindrical portion 65a of the support ring 65 radially outward. These fins 67 are joined to the support ring 65 integrally with the encoder 66 by vulcanization adhesion or the like. As a result, when the pulsar ring 64 rotates together with the inner ring 56 along with the rotation of the wheel, these fins 67 rotate like a windmill to positively convection the surrounding air and cool the bearing, and in the cap 61. It is possible to prevent the rainwater that has entered from scattering and staying in the seal 60 part. Therefore, it is possible to provide a wheel bearing device that provides added value to the pulsar ring 64 and can improve the sealing performance without disposing the seal 60 having a strong sealing performance (for example, Patent Documents). 1).

JP 2009-133357 A

  In such a conventional wheel bearing device, since the pulsar ring 64 and the inner seal 60 are separated, the number of parts is increased, the assembly work becomes complicated, and the cost reduction is hindered. , Compaction was hindered.

  The present invention has been made in view of such circumstances, and it is for a wheel that provides added value to a component and can improve the sealing performance without providing a seal having a strong sealing performance. An object is to provide a bearing device.

  In order to achieve such an object, the invention according to claim 1 of the present invention includes an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and an outer rolling of the double row on the outer periphery. An inner member in which a double-row inner rolling surface facing the surface is formed, and a double-row rolling element housed between the inner member and the outer member via a cage so as to be freely rollable, A seal mounted on both side openings of an annular space formed between the outer member and the inner member, and a slinger and an annular seal plate in which inner seals of these seals are arranged to face each other; In the wheel bearing device constituted by a pack seal comprising: a cylindrical portion in which the slinger is formed into a substantially L-shaped section by pressing from a steel plate and is press-fitted into the outer diameter of the inner member; and the cylinder And a standing plate portion extending radially outward from the portion, and the seal plate is A metal core fitted into the end of the material, and integrally bonded to the metal core by vulcanization, extending radially outwardly, and extending in a predetermined axial direction on the side surface of the standing plate portion of the slinger The seal member is provided with a side lip that is slidably contacted through a shimoshiro, and the seal member wraps around and joins the outer diameter of the end of the cored bar formed to have a reduced diameter, and is elastically deformed to the outer member. The seal plate and the outer edge of the slinger standing plate portion are opposed to each other through a slight radial clearance to form a labyrinth seal, and the opposed seal plate and slinger A plurality of cut grooves are formed in the circumferential direction at either corner.

  In this way, the slinger constituting the pack seal is formed into a substantially L-shaped cross section by pressing from a steel plate, and is pressed into the outer diameter of the inner member, and radially outward from this cylindrical portion. The core plate is fitted into the end portion of the outer member, and the core plate is integrally joined to the core bar by vulcanization adhesion, and extends inclining radially outward. A sealing member having a side lip that is in sliding contact with a side surface of a slinger standing plate through a predetermined axial squeezing, and this sealing member has an outer diameter at the end of the core bar formed by reducing the diameter. The elastic plate is provided with an elastic fitting portion that is wrapped around and joined and elastically deformed and pressure-bonded to the outer member, and the outer edge of the standing plate portion of the slinger is opposed through a slight radial clearance, The labyrinth seal is configured, and the opposing seal plate and slinger Since a plurality of cut grooves are formed in the circumferential direction at one of the corners, when the slinger or seal plate rotates together with the rotating side member as the wheel rotates, the surrounding air is positively moved by these cut grooves. It can be convected radially outward and the rainwater etc. entering the labyrinth seal part can be blown away, providing added value to the seal and sealing without having to provide a strong seal. It is possible to provide a wheel bearing device capable of improving the performance.

  Further, as in the second aspect of the present invention, a magnetic encoder is integrally vulcanized and bonded to the side surface of the standing plate portion of the slinger, and the magnetic encoder is mixed with elastomer powder and alternately in the circumferential direction. In addition, the magnetic poles N and S may be magnetized, and the cut groove may be formed in a corner portion of the outer diameter portion of the magnetic encoder.

  According to a third aspect of the present invention, the end surface of the seal plate and the side surface of the magnetic encoder are set to be substantially flush with each other, and the cut groove is formed to be inclined toward the outer diameter side. If the inclination angle is set to 45 ° or less, the convection of the air generated by the cut groove is directed to the inner side, and it is possible to improve the muddy water resistance by promoting the discharge of muddy water and the like.

  Preferably, as in the invention described in claim 4, if the cut groove is set so as not to be in the detection range of the rotational speed sensor of the magnetic encoder, the magnetic characteristics are not adversely affected and stable. Speed detection.

  Further, as in the invention described in claim 5, a taper surface having a predetermined inclination angle gradually expanding toward the opening is formed on the inner peripheral surface of the elastic fitting portion, and the width of the taper surface Is set so as to be larger than the width of the cut groove, even when there is muddy water that is not directly blown outward, the taper surface can be surely collided and smoothly guided to the outside. This can further improve the muddy water resistance.

  Further, as in the invention described in claim 6, a core part of the seal plate is formed into a substantially L-shaped cross section by pressing from a steel plate, and a cylindrical part that is metal-fitted to the outer member; An inner diameter portion extending radially inward from the cylindrical portion may be provided, and the cut groove may be formed in the inner diameter of the end portion of the elastic fitting portion.

  Further, as in the invention described in claim 7, the end surface of the seal plate and the side surface of the standing plate portion of the slinger are set to be substantially flush with each other, and the cut groove is inclined toward the inner diameter side. If formed and this inclination angle is set to 45 ° or less, the convection of air generated by the cut groove is directed to the inner side, and it is possible to improve the mud water resistance by promoting the discharge of muddy water and the like. it can.

  Preferably, as in the invention described in claim 8, if the width of the cut groove is set to be smaller than the plate thickness of the standing plate portion, the muddy water splashed by the cut groove is passed through the labyrinth seal. It can be prevented from being drawn into the seal and can be smoothly guided to the outside, and the muddy water resistance can be improved.

  Further, as in the ninth aspect of the invention, when the seal includes a pair of the side lips in the radial direction, the sealing torque can be reduced while maintaining the sealing performance.

  Further, as in the invention described in claim 10, the inner member integrally has a wheel mounting flange for mounting a wheel at one end, and faces one of the double row outer rolling surfaces on the outer periphery. An inner rolling surface, a hub wheel formed with a small-diameter step portion extending in the axial direction from the inner rolling surface, and a small-diameter step portion of the hub wheel are press-fitted to the other of the double-row outer rolling surface. The slinger may be formed by an inner ring formed with opposing inner rolling surfaces, and the slinger may be press-fitted into the outer diameter of the inner ring.

  The wheel bearing device according to the present invention includes an outer member in which a double row outer rolling surface is integrally formed on an inner periphery, and a double row inner rolling that faces the outer rolling surface of the double row on an outer periphery. An inner member having a surface formed thereon, a double-row rolling element that is rotatably accommodated between the inner member and the outer member via a cage, and the outer member and the inner member. For a wheel constituted by a seal mounted on both side openings of an annular space formed between them, and a pack seal in which an inner seal among these seals is composed of a slinger and an annular seal plate arranged to face each other In the bearing device, the slinger is formed into a substantially L-shaped section by pressing from a steel plate, and a cylindrical portion that is press-fitted into the outer diameter of the inner member, and a standing plate that extends radially outward from the cylindrical portion. A cored bar that is fitted into the end of the outer member. A seal member which is integrally joined to the metal core by vulcanization adhesion, extends in a radially outward direction, and includes a side lip which is in sliding contact with a side surface of the standing plate portion of the slinger via a predetermined axial direction The seal member is provided with an elastic fitting portion that is joined around the outer diameter of the end portion of the cored bar formed to have a reduced diameter, and is elastically deformed and pressure-bonded to the outer member. The seal plate and the outer edge of the slinger stand plate face each other with a slight radial clearance to form a labyrinth seal, and a notch groove is formed at one of the corners of the seal plate and slinger facing each other. Since the slinger or seal plate rotates together with the rotating side member as the wheel rotates, the surrounding air is positively convected radially outward by these cut grooves, and the labyrinth For wheels that can repel rainwater that is about to infiltrate from the wheel, add value to the seal, and improve sealability without the need for a separate seal with a strong seal A bearing device can be provided.

It is a longitudinal section showing one embodiment of a wheel bearing device concerning the present invention. It is a principal part enlarged view which shows the seal part of FIG. FIG. 3 is a view taken in the direction of arrow III in FIG. 2. It is sectional drawing which shows the modification of the seal | sticker of FIG. It is sectional drawing which shows the modification of the seal | sticker of FIG. It is sectional drawing which shows the other modification of the seal | sticker of FIG. It is a VII arrow line view of FIG. It is a longitudinal cross-sectional view which shows the conventional wheel bearing apparatus.

  An outer member integrally having a vehicle body mounting flange to be attached to the vehicle body on the outer periphery, a double row outer rolling surface formed integrally on the inner periphery, and a wheel mounting flange for mounting a wheel on one end A hub wheel integrally formed and having an inner rolling surface facing one of the outer rolling surfaces of the double row on the outer periphery, and a small-diameter step portion extending in the axial direction from the inner rolling surface, and the hub wheel An inner member comprising an inner ring that is press-fitted into a small diameter step portion and formed with the other inner rolling surface opposite to the double row outer rolling surface, and a cage between the inner member and the outer member. A double row rolling element housed in a freely rotatable manner via a seal, a seal mounted on both side openings of an annular space formed between the outer member and the inner member, and an inner of these seals The side seal is composed of a slinger and an annular seal plate arranged to face each other In the wheel bearing device constituted by a hook seal, the slinger is formed into a substantially L-shaped cross section by pressing from a steel plate and is press-fitted into the outer diameter of the inner ring, and radially outward from the cylindrical portion. The seal plate is integrally joined to the end of the outer member by vulcanization bonding and inclined radially outward. And a sealing member having a side lip that is in sliding contact with a side surface of the slinger standing plate portion via a predetermined axial squeezing, and the sealing member is formed by reducing the diameter of the core bar. An elastic fitting portion is provided that wraps around and joins the outer diameter of the end portion and is elastically deformed and pressure-bonded to the outer member, and has a slight radial clearance between the seal plate and the outer edge of the standing plate portion of the slinger. Through which the labyrinth seal is configured, A magnetic encoder is integrally vulcanized and bonded to the side surface of the standing plate portion of the slinger. This magnetic encoder is mixed with magnetic powder in the elastomer, and magnetic poles N and S are alternately magnetized in the circumferential direction. A cut groove is formed at a corner portion of the outer diameter portion so as to be inclined to 45 ° or less on the outer diameter side.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention, FIG. 2 is an enlarged view of a main part showing a seal part of FIG. 1, and FIG. 4 is a cross-sectional view showing a modification of the seal in FIG. 2, FIG. 5 is a cross-sectional view showing a modification of the seal in FIG. 4, and FIG. 6 is a cross-sectional view showing another modification of the seal in FIG. 7 is a view taken along arrow VII in FIG. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).

  This wheel bearing device is for a driven wheel referred to as a third generation, and is a double row rolling element housed in a freely rollable manner between the inner member 1 and the outer member 2, and both members 1 and 2. (Balls) 3 and 3. The inner member 1 includes a hub ring 4 and an inner ring 5 press-fitted into the hub ring 4 through a predetermined shimiro.

  The hub wheel 4 integrally has a wheel mounting flange 6 for mounting a wheel (not shown) at an end portion on the outer side, and has one (outer side) inner rolling surface 4a on the outer periphery and the inner rolling surface. A small diameter step 4b extending in the axial direction from the surface 4a is formed. Hub bolts 7 are planted on the wheel mounting flange 6 at equal intervals in the circumferential direction.

  The inner ring 5 is formed by forming the other (inner side) inner rolling surface 5a on the outer periphery and press-fitting into the small-diameter step portion 4b of the hub wheel 4 and plastically deforming the end portion of the small-diameter step portion 4b. It is fixed in the axial direction by the caulking portion 8.

  The hub wheel 4 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the inner raceway surface 4a and the inner side base portion 6a of the wheel mounting flange 6 to the small diameter step portion 4b. Thus, the surface hardness is set to a range of 58 to 64 HRC by induction hardening. Note that the caulking portion 8 is left with a raw surface hardness after forging. This has sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 6, improves the fretting resistance of the small-diameter stepped portion 4b serving as the fitting portion of the inner ring 5, and performs caulking. There is no occurrence of minute cracks or the like during processing, and the plastic processing of the crimped portion 8 can be performed smoothly. The inner ring 5 and the rolling element 3 are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC to the core part by quenching.

  The outer member 2 integrally has a vehicle body mounting flange 2b to be attached to a knuckle (not shown) on the outer periphery, and double row outer rolling surfaces 2a and 2a are formed on the inner periphery. That is, the outer-side outer rolling surface 2a facing the inner rolling surface 4a of the hub wheel 4 and the inner-side outer rolling surface 2a facing the inner rolling surface 5a of the inner ring 5 are integrally formed. . Double-row rolling elements 3 and 3 are accommodated between these rolling surfaces and are held by the cages 9 and 9 so as to roll freely.

  The outer member 2 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 2a and 2a have a surface hardness of 58 to 64 HRC by induction hardening. Has been cured. Seals 10 and 11 are attached to the opening of the annular space formed between the outer member 2 and the inner member 1, and leakage of grease sealed inside the bearing and rainwater from the outside. And dust are prevented from entering the bearing.

  The outer seal 10 includes a core 12 pressed into the inner periphery of the outer end of the outer member 2 via a predetermined shimiro, and a seal member integrally joined to the core 12 by vulcanization adhesion. 13 is an integral seal. The metal core 12 is formed in a substantially L-shaped cross section by press working from an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a cold rolled steel plate (JIS standard SPCC type or the like).

  On the other hand, the seal member 13 is made of a synthetic rubber such as NBR (acrylonitrile-butadiene rubber), is formed to be inclined radially outward, and is in sliding contact with a base portion 6a having a circular cross section in a predetermined axial direction. It has a side lip 13a, a dust lip 13b, and a grease lip 13c formed so as to be inclined toward the inner side of the bearing, and slidably contacted with the base 6a via a predetermined radial shimiro.

  In addition to NBR, the material of the seal member 13 is excellent in heat resistance and chemical resistance, such as HNBR (hydrogenated acrylonitrile butadiene rubber), EPDM (ethylene propylene rubber), etc., which have excellent heat resistance. Examples thereof include ACM (polyacrylic rubber), FKM (fluororubber), and silicon rubber.

  Here, as shown in an enlarged view in FIG. 2, the inner-side seal 11 is configured by a so-called pack seal including a slinger 14 and an annular seal plate 15 arranged to face each other. The slinger 14 is formed into a substantially L-shaped cross section by pressing from a ferromagnetic steel plate, for example, a ferritic stainless steel plate (JIS standard SUS430 series, etc.) or a rust-proof cold rolled steel plate. The cylindrical portion 14a is press-fitted into the outer diameter of the inner ring 5, and the upright plate portion 14b extends radially outward from the cylindrical portion 14a.

  A magnetic encoder 16 in which a magnetic powder such as ferrite is mixed in an elastomer such as rubber is integrally vulcanized and bonded to the inner side surface of the standing plate portion 14b. The magnetic encoder 16 is magnetized with magnetic poles N and S alternately in the circumferential direction to constitute a rotary encoder for detecting the rotational speed of the wheel.

  On the other hand, the seal plate 15 includes a cored bar 17 fitted into the end of the outer member 2 and a seal member 18 integrally joined to the cored bar 17 by vulcanization adhesion. The metal core 17 is formed of an austenitic stainless steel plate or a cold-rolled steel plate that has been rust-proofed by a pressing process so that the cross-section is substantially L-shaped, and a cylindrical portion 17a that is metal-fitted to the outer member 2. And an inner diameter part 17b extending radially inward from the cylindrical part 17a.

  The seal member 18 is made of a synthetic rubber such as NBR, and has a side lip 18a extending obliquely outward in the radial direction, and a grease lip 18b and a dust lip 18c formed in a bifurcated shape on the inner diameter side. The side lip 18a is in sliding contact with a side surface on the outer side of the standing plate portion 14b of the slinger 14 via a predetermined axial shimiro, and the grease lip 18b and the dust lip 18c are in contact with the cylindrical portion 14a via a predetermined radial shimiro. Are in sliding contact.

  The sealing member 18 is joined so as to cover the surface of the cored bar 17, and in particular, the sealing member 18 wraps around and joins to the end of the cylindrical part 17 a formed by reducing the outer diameter. A portion 18d is formed. The elastic fitting portion 18d is pressure-bonded by the elastic deformation of the seal member 18 to the outer member 2, thereby enhancing the airtightness of the fitting portion. The elastic fitting portion 18d and the outer edge of the magnetic encoder 16 are opposed to each other through a slight radial clearance, and a labyrinth seal 19 is configured. In addition to the exemplified NBR, examples of the material of the seal member 18 include ACM, FKM, or silicone rubber having excellent heat resistance and chemical resistance, such as HNBR and EPDM having excellent heat resistance. can do.

  Here, in this embodiment, a plurality of cut grooves 20 are formed in the circumferential direction at the corners of the outer diameter portion of the magnetic encoder 16 (see FIG. 3). Thus, when the slinger 14 rotates together with the inner ring 5 as the wheel rotates, the surrounding air is actively convected radially outward by the cut grooves 20, and rainwater or the like is about to enter from the labyrinth seal 19 part. It is possible to provide a wheel bearing device that can add value to the seal 11 and can improve the sealing performance without separately providing a seal having a strong sealing performance. . In addition, it is preferable that the cut groove 20 does not reach the detection range S of the rotation speed sensor 21 so as not to adversely affect the magnetic characteristics.

  A seal 22 shown in FIG. 4 is a modification of the seal 11 described above. In addition, the same code | symbol is attached | subjected to the component and site | part which has the same component same part as embodiment mentioned above, or the same function, and detailed description is abbreviate | omitted.

  The seal 22 is constituted by a pack seal composed of a slinger 14 and an annular seal plate 23 arranged to face each other. Similarly to the above-described embodiment, a magnetic encoder 24 in which a magnetic substance powder such as ferrite is mixed with an elastomer such as rubber is integrally vulcanized and bonded to the side surface on the inner side of the standing plate portion 14 b of the slinger 14. Yes. In the magnetic encoder 24, magnetic poles N and S are alternately magnetized in the circumferential direction.

  The seal plate 23 includes a cored bar 17 fitted into the end of the outer member 2 and a seal member 18 ′ integrally joined to the cored bar 17 by vulcanization adhesion. The seal member 18 'is made of a synthetic rubber such as NBR, and has a side lip 18a extending obliquely outward in the radial direction, and a grease lip 18b and a dust lip 18c formed in a bifurcated shape on the inner diameter side. Yes. Then, the seal member 18 ′ is wrapped around and joined to the end of the cylindrical portion 17 a of the core bar 17 to form an elastic fitting portion 18 e, and the elastic fitting portion 18 e and the outer edge of the magnetic encoder 24 are slightly in the radial direction. A labyrinth seal 19 is configured to face each other through a gap.

  Here, in the present embodiment, the end surface of the seal plate 23 and the side surface of the magnetic encoder 24 are set to be substantially flush with each other, and the cut grooves 25 are formed in the corners of the outer diameter portion of the magnetic encoder 24 in the circumferential direction. A plurality are formed. The inclination angle θ1 of the cut groove 25 is set to 45 ° or less, preferably 10 ° <θ1 <45 °. Thereby, the convection of the air which generate | occur | produces with the notch groove 25 turns to an inner side, becomes force which promotes discharge | emission of muddy water, etc., and can improve muddy water resistance. The term “substantially equal” as used herein means, for example, a design target value that is substantially free of steps, that is, a step caused by a processing error or the like should be allowed.

  Further, a tapered surface 26 having an inclination angle θ2 that gradually increases in diameter toward the opening is formed on the inner peripheral surface of the elastic fitting portion 18e of the seal member 18 ′, and the axial width W1 of the tapered surface 26 is cut. It is set to be larger than the axial width W2 of the groove 25 (W1> W2). As a result, even when there is muddy water that is not directly blown outward, it can be surely collided with the tapered surface 26 and smoothly guided to the outside, and the mud water resistance can be further improved. The inclination angle θ2 of the tapered surface 26 is set in a range of 0 <θ2 <10 °. In addition, when the inclination angle θ2 is 10 ° or more, it is not preferable because muddy water or the like returns to the labyrinth seal 19 from the outside and easily enters.

  FIG. 5 shows a modification of the seal 22. In addition, the same code | symbol is attached | subjected to the component and site | part which has the same component same part as embodiment mentioned above, or the same function, and detailed description is abbreviate | omitted.

  The seal 27 is composed of a pack seal composed of a slinger 14 and an annular seal plate 28 arranged to face each other. Similarly to the above-described embodiment, a magnetic encoder 24 in which a magnetic substance powder such as ferrite is mixed with an elastomer such as rubber is integrally vulcanized and bonded to the side surface on the inner side of the standing plate portion 14 b of the slinger 14. Yes.

  The seal plate 28 includes a cored bar 17 fitted into the end of the outer member 2 and a seal member 29 integrally joined to the cored bar 17 by vulcanization adhesion. The seal member 29 is made of a synthetic rubber such as NBR, and has a pair of side lips 29a and 29b extending obliquely outward in the radial direction, and a grease lip 29c extending inclined toward the bearing inward side on the inner diameter side. doing. Then, the sealing member 29 wraps around and joins the end of the cylindrical portion 17a of the core metal 17 to form an elastic fitting portion 18e, and the elastic fitting portion 18e and the outer edge of the magnetic encoder 24 have a slight radial clearance. The labyrinth seal 19 is configured to face each other.

  In this embodiment, the end face of the seal plate 28 and the side surface of the magnetic encoder 24 are set to be substantially flush with each other as in the above-described embodiment, and the cut groove 25 is formed in the corner of the outer diameter portion of the magnetic encoder 24. Since a plurality of the lips are formed in the direction, the muddy water resistance can be improved and a pair of side lips are provided in place of the dust seal, so that the seal torque can be reduced while maintaining the sealing performance.

  FIG. 6 shows a modification of the seal 22. In addition, the same code | symbol is attached | subjected to the component and site | part which has the same component same part as embodiment mentioned above, or the same function, and detailed description is abbreviate | omitted.

  The seal 30 is constituted by a pack seal composed of a slinger 31 and an annular seal plate 32 arranged to face each other. The slinger 31 is formed from an austenitic stainless steel plate or a cold-rolled steel plate that has been rust-proofed into a substantially L-shaped section by press working, and is press-fitted into the outer diameter of an inner ring (not shown) serving as a fixed member. The cylindrical portion 31a and a standing plate portion 31b extending radially outward from the cylindrical portion 31a. The end portion of the cylindrical portion 31a is formed in a spire shape to prevent a dust strip 34c, which will be described later, from coming into contact with the corner portion during assembly and being damaged.

  On the other hand, the seal plate 32 includes a cored bar 33 fitted into an end of an outer member (not shown) serving as a rotation side member, and a seal member 34 integrally joined to the cored bar 33 by vulcanization adhesion. It consists of. The cored bar 33 is formed of an austenitic stainless steel plate or a cold-rolled steel plate that has been rust-proofed by a pressing process so that the cross section is substantially L-shaped, and a cylindrical portion 33a that is metal-fitted to the outer member; And an inner diameter portion 33b extending radially inward from the cylindrical portion 33a.

  As in the above-described embodiment, the sealing member 34 wraps around and joins the end of the cylindrical portion 33a of the core metal 33 to form an elastic fitting portion 34d. And the elastic fitting part 34d and the outer edge of the standing board part 31b of the slinger 31 oppose via a slight radial clearance, and the labyrinth seal 35 is comprised.

  Here, in the present embodiment, the end surface of the seal plate 32 and the side surface of the standing plate portion 31b of the slinger 31 are set so as to be substantially flush with each other and cut into the corner portion of the inner diameter of the end portion of the elastic fitting portion 34d. A plurality of grooves 36 are formed in the circumferential direction (see FIG. 7). The inclination angle θ3 of the cut groove 36 is set to 45 ° or less, preferably 10 ° <θ3 <45 °. Thereby, the convection of the air which generate | occur | produces by the notch groove 36 turns to an inner side, becomes a force which encourages discharge | emission of muddy water, etc., and can improve muddy water resistance.

  Furthermore, the axial width W3 of the cut groove 36 is set to be smaller than the plate thickness W4 of the upright plate portion 31b (W3 <W4). Thereby, it is possible to prevent the muddy water splashed by the cut groove 36 from being drawn into the seal 30 through the labyrinth seal 35 and smoothly guide it to the outside, thereby improving the mud water resistance. .

  The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, 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 indicated 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.

  The wheel bearing device according to the present invention can be applied to a wheel bearing device having a first to third generation structure provided with a pack seal.

DESCRIPTION OF SYMBOLS 1 Inner member 2 Outer member 2a Outer rolling surface 2b Car body mounting flange 3 Rolling body 4 Hub wheel 4a, 5a Inner rolling surface 4b Small diameter step part 5 Inner ring 6 Wheel mounting flange 6a Base 7 on the inner side of the wheel mounting flange Hub bolt 8 Clamping section 9 Cage 10 Outer side seals 11, 22, 27, 30 Inner side seals 12, 17, 33 Core bars 13, 18, 18 ', 29, 34 Seal members 13a, 18a, 29a, 29b 34a Side lip 13b, 18c, 34c Dustrip 13c, 18b, 29c, 34b Grease lip 14, 31 Slinger 14a, 17a, 31a, 33a Cylindrical part 14b, 31b Standing plate part 15, 23, 28, 32 Seal plate 16, 24 Magnetic encoder 17b, 33b Inner diameter part 18d, 18e, 34d Elastic fitting part 19, 35 Labyrinth seal 0, 25, 36 Cut groove 21 Rotational speed sensor 26 Tapered surface 51 Outer member 51a Outer rolling surface 51b Car body mounting flange 52 Inner member 53 Ball 54 Wheel mounting flange 55 Hub wheels 55a, 56a Inner rolling surface 55b Small diameter step Part 56 Inner ring 57 Cage 58 Clamping part 59 Outer side seal 60 Inner side seal 61 Cap 62 Core metal 63 Cap body 64 Pulsar ring 65 Support ring 65a Cylindrical part 65b Standing plate part 66 Encoder 67 Fin S Detection range W1 Tapered surface Axial width W2, W3 Axial width W4 of the cut groove Plate thickness θ1, θ3 Inclination angle of the cut groove θ2 Inclination angle of the taper surface

Claims (10)

An outer member in which a double row outer rolling surface is integrally formed on the inner periphery;
An inner member in which a double row inner rolling surface facing the outer row rolling surface of the double row is formed on the outer periphery;
A double row rolling element housed between the inner member and the outer member via a cage to be freely rollable,
A seal mounted on both side openings of an annular space formed between the outer member and the inner member;
Among these seals, in the wheel bearing device constituted by a pack seal composed of a slinger and an annular seal plate arranged opposite to each other on the inner side,
The slinger is formed by pressing a steel plate into a substantially L-shaped cross section, and includes a cylindrical portion that is press-fitted into the outer diameter of the inner member, and a vertical plate portion that extends radially outward from the cylindrical portion. The sealing plate is a core metal fitted into the end of the outer member, and the core metal is integrally joined to the core metal by vulcanization adhesion, and extends in a radially outward direction. A seal member having a side lip that is in sliding contact with the side surface of the part via a predetermined axial shimiro,
The seal member includes an elastic fitting portion that is joined around the outer diameter of the end portion of the cored bar formed to have a reduced diameter, and is elastically deformed and pressure-bonded to the outer member.
The seal plate and the outer edge of the slinger stand plate face each other with a slight radial clearance to form a labyrinth seal, and a notch groove is formed at one of the corners of the seal plate and slinger facing each other. A bearing device for a wheel, wherein a plurality of the bearing devices are formed in a direction.   A magnetic encoder is integrally vulcanized and bonded to the side surface of the standing plate portion of the slinger, and this magnetic encoder is mixed with magnetic powder in the elastomer, and magnetic poles N and S are alternately magnetized in the circumferential direction. The wheel bearing device according to claim 1, wherein the cut groove is formed in a corner portion of an outer diameter portion of the magnetic encoder.   The end face of the seal plate and the side surface of the magnetic encoder are set to be substantially flush with each other, and the cut groove is formed to be inclined to the outer diameter side, and the inclination angle is set to 45 ° or less. The wheel bearing device according to claim 1 or 2.   The wheel bearing device according to claim 2 or 3, wherein the cut groove is set so as not to cover a detection range of a rotation speed sensor of the magnetic encoder.   A tapered surface having a predetermined inclination angle that gradually increases in diameter toward the opening is formed on the inner peripheral surface of the elastic fitting portion, and the width of the tapered surface is set to be larger than the width of the cut groove. The wheel bearing device according to claim 3 or 4, wherein the wheel bearing device is provided.   A cylindrical portion in which the metal core of the seal plate is formed into a substantially L-shaped section by pressing from a steel plate and is metal-fitted to the outer member, and an inner diameter portion extending radially inward from the cylindrical portion The wheel bearing device according to claim 1, wherein the cut groove is formed in an inner diameter of an end portion of the elastic fitting portion.   The end surface of the sealing plate and the side surface of the standing plate portion of the slinger are set so as to be substantially flush with each other, and the cut groove is formed to be inclined toward the inner diameter side, and the inclination angle is set to 45 ° or less. The wheel bearing device according to claim 1 or 6.   The wheel bearing device according to claim 7, wherein a width of the cut groove is set to be smaller than a plate thickness of the standing plate portion.   The wheel bearing device according to claim 1, wherein the seal includes a pair of the side lips in the radial direction.   From the inner rolling surface, the inner member integrally has a wheel mounting flange for mounting a wheel at one end, and is opposed to one of the outer rolling surfaces of the double row on the outer periphery. A hub wheel formed with a small-diameter step portion extending in the axial direction, and an inner ring formed with an inner rolling surface that is press-fitted into the small-diameter step portion of the hub wheel and faces the other of the outer rolling surfaces of the double row. The wheel bearing device according to claim 1, wherein the slinger is press-fitted into the outer diameter of the inner ring.

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