JP2008051289A - Bearing device for wheel - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device for a wheel with improved sealing performance by enhancing the airtightness of a seal fitting part. <P>SOLUTION: This bearing device for the wheel has seals 8, (9) installed in an opening of an annular space formed between an outer member 10 and an inner member 1. The seals 8, (9) are composed of core metals 15, (20) becoming the fitting of the outer member 10 and the fitting of mutual metals by forming a steel plate by press working, and seal members 16, (21) integrally joined to these core metals 15, (20) and having projection parts 16d, (21d) coveting an exposed part by projecting outside the outer peripheral surface of the core metals 15, (20). Predetermined hardening layers 13, (14) are formed over fitting surfaces 11, (12) of the seals 8, (9) from an outside rollingly traveling surface 10a of the outer member 10 by induction hardening. These hardening layers 13, (14) exceed cylindrical parts 15a, (20a) of the core metals 15, (20), and are fastened in the vicinity of end surfaces 10c, (10d) of the outer member 10. <P>COPYRIGHT: (C)2008,JPO&INPIT

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 more specifically, improves the airtightness of a fitting portion of a seal attached to the bearing portion and improves sealing performance. The present invention relates to a wheel bearing device.

  2. Description of the Related Art Conventionally, a wheel bearing device for supporting a wheel of an automobile or the like supports a hub wheel for mounting a wheel rotatably via a double row rolling bearing, and includes a drive wheel and a driven wheel. For structural reasons, an inner ring rotation method is generally used for driving wheels, and an inner ring rotation method and an outer ring rotation method are generally used for driven wheels. Further, the wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double row angular ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device. Second generation structure in which body mounting flange or wheel mounting flange is formed directly on the outer periphery of the member, third generation structure in which one inner rolling surface is directly formed on the outer periphery of the hub wheel, or hub wheel, etc. It is roughly classified into a fourth generation structure in which the inner rolling surface is directly formed on the outer periphery of the outer joint member of the speed universal joint.

  These bearing portions are fitted with seals to prevent leakage of grease sealed inside the bearings and to prevent intrusion of rainwater, dust and the like from the outside. In recent years, the maintenance of automobiles has become more maintenance-free, and even longer bearing life has been demanded for wheel bearing devices. However, there are many cases in which rainwater, dust, or the like intrudes into the bearing and damages the bearing due to a sealing failure or a decrease in sealing performance. Therefore, it is possible to improve the bearing life by improving the sealing performance of the seal.

  Conventionally, various seals with improved sealing performance have been proposed. A typical example of such a seal is shown in FIG. This seal 50 is attached to a housing 51 as two members concentrically and relatively rotatably assembled to each other, and a rotary shaft 52 inserted into the housing 51, and a sleeve that rotates integrally with the rotary shaft 52. The annular gap between the members 53 is sealed.

  The seal 50 includes a metal ring 54 having a hollow hole formed by pressing a metal plate material by pressing or the like, and an elastic member 55 in which rubber or the like is fixed to the metal ring 54 by baking or bonding. This elastic member 55 has a main lip 55 a as a part, and the main lip 55 a slidably contacts with the outer peripheral surface of the sleeve portion 53 b of the sleeve member 53, and between the housing 51 and the rotating shaft 52. The annular gap is sealed to the sealed fluid side O and the atmosphere side A. Further, a tongue-shaped dust lip 55b is provided continuously with the main lip 55a, extends to the atmosphere side A, and is formed so as to be slidably contacted with the flange portion 53a of the sleeve member 53 by tilting radially outward. The muddy water from the side A is prevented from entering the inside.

  The metal ring 54 has a cylindrical portion 54a extending in the axial direction and an annular portion 54b bent from the end of the cylindrical fluid 54a toward the inner diameter side from the end of the sealed fluid side O. The main lip 55a and the dust lip 55b are continuously fixed to the surface of the side A with the elastic lip 55a.

  And since the clearance gap between the outer peripheral surface of the sleeve member 53 and the inner peripheral surface of the housing 51 is small, it is difficult to ensure the space for providing the elastic member 55 in the outer peripheral surface of the cylindrical part 54a of the metal ring 54. The outer peripheral surface of the cylindrical portion 54 a is directly fitted to the inner peripheral surface of the housing 51, and the seal 50 is fixed to the housing 51.

  Here, a tapered portion 51a is provided at the edge of the opening of the housing 51, and the elastic member 55 further seals the tapered portion 51a in a predetermined range of the end portion on the atmosphere side A of the cylindrical portion 54a. The edge seal portion 55c is fixed as a part of the elastic member 55. FIG. 4 (b) shows an enlarged view of the edge seal portion 55c. The edge seal portion 55c has a portion protruding outward from the outer peripheral surface of the cylindrical portion 54a of the metal ring 54. The protruding portion seals the tapered portion 51 a of the opening of the housing 51. The shape of the protruding portion is made as similar as possible to the shape of the tapered portion 51a of the housing 51 so that the protruding portion when the seal 50 is attached to the housing 51 can easily follow the shape of the tapered portion 51a.

  The predetermined range is such that the contact area and the contact pressure according to the use environment can be secured by the width of the seal 50, the fitting between the housing 51 and the cylindrical portion 54a, etc., and the seal 50 does not come out of the housing 51. The width of the cylindrical portion 54 a is set in a range not covered with the elastic member 55.

  Further, a concave portion 54c is provided at the end surface portion of the cylindrical portion 54a of the metal ring 54 so that the elastic member 55 can be accurately fixed, and the base end portion of the edge seal portion 55c protrudes from the outer peripheral surface of the cylindrical portion 54a. When the seal 50 is attached to the housing 51, it is prevented from being peeled off.

By adopting such a configuration, the tapered portion 51 a that is normally provided at the edge of the opening facing the mounting portion of the seal 50 provided in the metal housing 51 is replaced with the edge seal portion 55 c of the elastic member 55 of the seal 50. Therefore, the leakage of the sealing fluid between the housing 51 and the seal 50 can be prevented.
JP 2004-18865 A

  Such a conventional seal 50 can improve the sealing performance between the seal 50 and the housing 51 to which the seal 50 is mounted. However, this type of seal 50 is caused by an increase in the internal pressure of the bearing during operation. It is mounted with a pressure input that provides a predetermined pulling strength so that it does not come out. In this case, when the metal ring 54 of the seal 50 is press-fitted into the housing 51, the fitting surface of the housing 51 may be scratched in the axial direction.

  Normally, the mating surface is ground to improve hermeticity and finished to the specified shape and accuracy. However, due to scratches that occur during press-fitting, muddy water or the like leaks or grease leaks from this mating surface. There is a fear. For example, as in the conventional seal 50, even if a part of the elastic member 55 such as rubber is covered up to the end of the metal ring 54 as the edge seal portion 55c, the elastic member 55 deteriorates over time, and the length It is difficult to maintain hermeticity over time.

  The present invention has been made in view of such a conventional problem, and an object of the present invention is to provide a wheel bearing device in which the airtightness of the seal fitting portion is improved and the sealing performance is improved.

  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 provided with a double row inner rolling surface facing the surface, and a double row accommodated between the rolling surfaces of the inner member and the outer member via a retainer. A rolling bearing group and a seal mounted on an opening of an annular space formed between the outer member and the inner member, wherein the seal presses the steel plate. The outer member and a metal core that are fitted to each other, and a seal member integrally joined to the metal core, and the seal fit from the outer rolling surface of the outer member. A predetermined hardened layer is formed by induction hardening over the mating surface, and this hardened layer extends beyond the fitting portion of the cored bar, and It is stopped in the vicinity of the end face of the member.

  Thus, in the wheel bearing device including the seal mounted on the opening of the annular space formed between the outer member and the inner member, the seal is formed by pressing a steel plate, It consists of a core bar that fits the metal member and metal, and a seal member that is integrally joined to the core bar, and induction hardening from the outer rolling surface of the outer member to the seal fitting surface A predetermined hardened layer is formed by this, and this hardened layer is stopped in the vicinity of the end face of the outer member beyond the fitting portion of the core metal, so that the strength is prevented by preventing the occurrence of burning cracks and cracks due to impact loads. In addition to securing, it is possible to prevent the streaks in the axial direction from being attached to the fitting surface by press-fitting the cored bar, and to ensure stable airtightness over a long period of time.

  Preferably, as in the invention described in claim 2, the counter portion of the outer rolling surface is abolished or reduced, and a groove bottom is secured to such an extent that the groove diameter of the outer rolling surface can be easily measured. If a smooth joint portion is formed between the bottom and the fitting surface, the quenching part can be smoothed, the cracking due to abnormal heating can be prevented, the range of the hardened layer can be easily controlled, and the desired range can be obtained. A quenching pattern can be obtained.

  Further, as in the invention described in claim 3, the core metal has a cylindrical portion that is press-fitted into the fitting surface via a predetermined scissors, and the seal member is more than the outer peripheral surface of the cylindrical portion. If the protrusion protrudes outward and is joined so as to cover the exposed portion of the metal core, the protrusion closes the opening of the fitting surface and further improves the airtightness of the seal fitting portion. Can be increased.

  Further, as in the invention described in claim 4, if the fitting surface is regulated to a predetermined accuracy by grinding, the air tightness of the seal fitting portion can be enhanced.

  Preferably, as in the fifth aspect of the present invention, when the fitting surface is simultaneously ground with the outer rolling surface by a general-purpose grindstone, the coaxiality of the fitting surface can be obtained, and the seal is airtight. Can be further enhanced.

  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 provided with a surface, a double row rolling element group rotatably accommodated between both rolling surfaces of the inner member and the outer member via a cage, and the outer member And a seal mounted on an opening in an annular space formed between the inner member and the inner member, wherein the seal is formed by pressing a steel plate, and the outer member and the metal It consists of a metal core that is fitted to each other and a seal member that is integrally joined to the metal core, and is predetermined by induction hardening from the outer rolling surface of the outer member to the seal engagement surface. The hardened layer is formed, and the hardened layer is stopped in the vicinity of the end surface of the outer member beyond the fitting portion of the cored bar. Therefore, it prevents cracking due to burning cracks and impact loads and secures strength, and prevents the streaks in the axial direction from being attached to the mating surface by press-fitting the core metal, and is stable for a long period of time. Airtightness can be ensured.

  A body mounting flange for mounting to the suspension device on the outer periphery is integrated, an outer member with a double row outer raceway formed on the inner periphery, and a wheel mounting flange for mounting a wheel on one end A hub wheel having an outer periphery and one inner rolling surface facing the outer rolling surface of the double row, and a small-diameter step portion extending in an 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 has the other inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and both rolling of the inner member and the outer member. A double row rolling element group that is slidably accommodated between the running surfaces via a cage, and a seal that is attached to an opening of an annular space formed between the outer member and the inner member; In the wheel bearing device comprising: the seal is formed by pressing a steel plate, and the outer side A metal core and a metal core, and a seal member that is integrally joined to the metal core and has a protruding portion that covers an exposed portion that protrudes outward from the outer peripheral surface of the metal core, A predetermined hardened layer is formed by induction quenching from the outer rolling surface of the outer member to the fitting surface of the seal, and this hardened layer exceeds the fitting portion of the metal core, and the outer member It is stopped in the vicinity of the end face.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention, FIG. 2A is an enlarged view of a main part showing a seal fitting portion on the outer side of FIG. 1, and FIG. ) Is a main part enlarged view showing the inner side seal fitting part, FIG. 3 is a modified example of FIG. 2, and (a) is a main part enlarged view showing the outer side seal fitting part, (B) is a principal part enlarged view which shows the seal fitting part by the side of an inner side. 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 the outer side (left side in the drawing), and the side closer to the center is referred to as the inner side (right side in the drawing).

  This wheel bearing device is for a drive wheel, and includes an inner member 1 and an outer member 10, and double row rolling elements (balls) 7, 7 group accommodated between the members 1, 10 so as to roll freely. It has a configuration called the third generation. The inner member 1 includes a hub ring 2 and an inner ring 3 that is press-fitted into the hub ring 2 through a predetermined scissors.

  The hub wheel 2 integrally has a wheel mounting flange 4 for mounting a wheel at one end portion, one (outer side) inner rolling surface 2a on the outer periphery, and a cylinder extending in the axial direction from the inner rolling surface 2a. A small diameter step 2b is formed, and a serration (or spline) 2c for torque transmission is formed on the inner periphery. Further, hub bolts 5 are planted in the circumferentially equidistant positions of the wheel mounting flanges 4. Further, the inner ring 3 has the other (inner side) inner raceway surface 3a formed on the outer periphery.

  The hub wheel 2 is made of medium and high carbon steel containing carbon of 0.40 to 0.80 wt% such as S53C, and the wheel mounting flange 4 serving as a seal land portion of the outer side seal 8 to be described later, including the inner rolling surface 2a. The surface is hardened in the range of 58 to 64 HRC by induction hardening from the base 4a to the small diameter step 2b. On the other hand, the inner ring 3 and the rolling element 7 are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC up to the core part by quenching.

  The outer member 10 integrally has a vehicle body mounting flange 10b to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and the inner rolling surfaces 2a and 3a of the inner member 1 on the inner periphery. Opposing double-row outer rolling surfaces 10a and 10a are integrally formed. Between these rolling surfaces 10a, 2a and 10a, 3a, a double-row rolling element 7, 7 group is accommodated via a cage 6 so as to roll freely. The outer member 10 is formed of medium-high carbon steel containing carbon 0.40 to 0.80 wt% such as S53C, and the fitting surface 11 on which the double row outer rolling surfaces 10a and 10a and the seals 8 and 9 are mounted. 12, predetermined hardened layers 13 and 14 in the range of 58 to 64 HRC are formed on the surface by induction hardening.

  Seals 8 and 9 are attached to both ends of the outer member 10 to seal the opening of the annular space formed between the outer member 10 and the inner member 1. The seals 8 and 9 prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater and dust from the outside into the bearing. Here, a double-row angular contact ball bearing using balls as the rolling elements 7 is illustrated, but the present invention is not limited to this, and a double-row tapered roller bearing using tapered rollers as the rolling elements 7 may be used. .

  Here, the seal 8 on the outer side of the seals 8 and 9 is, as shown in an enlarged view in FIG. 2 (a), a core 15 and a seal integrally joined to the core 15 by vulcanization adhesion or the like. Member 16. The core 15 is made of austenitic stainless steel plate (JIS standard SUS304, etc.) or a rust-proof cold rolled steel plate (JIS standard SPCC, etc.), etc. A cylindrical portion 15a that is formed in a letter shape and is press-fitted into the fitting surface 11 of the outer member 10 via a predetermined shimiro, and an inner portion 15b that extends radially inward from the cylindrical portion 15a. Thus, since the metal core 15 is formed from the steel plate which has a rust prevention ability, rusting can be prevented over a long period of time and the durability of the seal 8 can be improved.

  The seal member 16 is made of an elastic member such as nitrile rubber, and has a pair of side lips 16a and 16b and a radial lip 16c that are in sliding contact with a base portion 4a having a circular cross section. The side lips 16a and 16b are formed to be inclined radially outward toward the tip, and the tip is in sliding contact with the base portion 4a with a predetermined squeeze to prevent rainwater, dust, etc. from entering the bearing from the outside. is doing. Further, the radial lip 16c is formed such that the tip thereof is inclined toward the inner side of the bearing, thereby preventing the grease enclosed in the bearing from leaking to the outside.

  The seal member 16 has a protruding portion 16 d that protrudes outward from the outer peripheral surface of the cylindrical portion 15 a of the core metal 15 and is joined so as to cover the exposed portion of the core metal 15. This protrusion 16 d closes the opening of the fitting surface 11. Thereby, the airtightness of the fitting part of the seal | sticker 8 can be improved.

  Here, in the present embodiment, as described above, the predetermined hardened layer 13 is formed from the outer side outer rolling surface 10 a to the fitting surface 11 of the seal 8 via the counter portion 17. The hardened layer 13 is stopped in the vicinity of the outer end face 10c of the outer member 10 beyond the cylindrical portion 15a of the cored bar 15. And the fitting surface 11 of the outer member 10 used as a fitting between the metal core 15 and the metal is simultaneously ground with the outer rolling surface 10a by a general-purpose grindstone, and is regulated to a predetermined accuracy. As a result, strength is ensured by preventing cracking due to burning cracks and impact loads, and the fitting surface 11 is prevented from being scratched in the axial direction by the press-fitting of the core metal 15 and is simultaneously ground. The coaxiality of the fitting surface 11 is obtained, and stable airtightness can be ensured over a long period of time. Furthermore, even if the protruding portion 16d of the seal member 16 deteriorates over time, the airtightness is not impaired. Here, the counter portion 17 is a convex portion formed by protruding a predetermined amount from the groove bottom of the outer rolling surface 10a so that the rolling element 7 fitted to the outer rolling surface 10a does not fall off at the time of bearing assembly. Point to.

  On the other hand, the seal 9 on the inner side is composed of a slinger 18 and an annular seal plate 19 arranged to face each other as shown in an enlarged view in FIG. Slinger 18 has a substantially L-shaped cross section when it is pressed from a ferritic stainless steel plate (JIS standard SUS430, etc.) or a rust-proof cold rolled steel plate (JIS standard SPCC, etc.). The cylindrical portion 18a is press-fitted into the inner ring 3 and the upright plate portion 18b extends radially outward from the cylindrical portion 18a. Thereby, the rusting of the slinger 18 can be prevented and the durability of the seal 9 can be improved.

  The seal plate 19 has a substantially L-shaped cross section and is attached to the outer member 10. The seal plate 19 includes a core metal 20 and a seal member 21 integrally joined to the core metal 20 by vulcanization adhesion or the like. The core 20 is formed by press working from an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a rust-proof cold rolled steel plate (JIS standard SPCC type or the like). The cylindrical portion 20a is press-fitted into the fitting surface 12 of the member 10 via a predetermined shimiro, and the upright plate portion 20b extends radially inward from the cylindrical portion 20a.

  The seal member 21 is made of an elastic member such as nitrile rubber, and includes a side lip 21a that is in sliding contact with the standing plate portion 18b of the slinger 18 and radial lips 21b and 21c that are in sliding contact with the cylindrical portion 18a. The side lip 21a is formed so as to be inclined to the outer diameter side from the upright plate portion 20b of the core metal 20, and the tip is slidably contacted with the upright plate portion 18b of the slinger 18 with a predetermined squeezing force so that rainwater, dust, etc. To prevent intrusion. Further, the radial lips 21b, 21c formed in a bifurcated shape are in sliding contact with the cylindrical portion 18a of the slinger 18 with a predetermined squeeze, and the intrusion of rainwater, dust, etc. that has entered through the side lip 21a and the inside of the bearing. Prevents leakage of enclosed grease to the outside.

  Further, the sealing member 21 has a protruding portion 21d that wraps around the outer surface of the end portion of the cylindrical portion 20a of the core metal 20 and protrudes outside the outer peripheral surface, and is joined so as to cover the exposed portion of the core metal 20. ing. The protruding portion 21d is brought into close contact with the opening of the fitting surface 12 to improve airtightness. Further, a labyrinth seal is formed by allowing the outer edge of the standing plate portion 18b of the slinger 18 and the cored bar 20 to face each other through a slight radial clearance, thereby preventing rainwater, dust, etc. from directly falling on the side lip 21a from the outside. And improve the sealing performance.

  Here, a predetermined hardened layer 14 is formed over the fitting surface 12 of the seal 9 from the outer side rolling surface 10a on the inner side through the counter portion 22. This hardened layer 14 is stopped in the vicinity of the inner side end face 10d of the outer member 10 beyond the cylindrical portion 20a of the cored bar 20 like the outer hardened layer 13 described above. And the fitting surface 12 of the outer member 10 used as a fitting between the metal core 20 and the metal is simultaneously ground with the outer rolling surface 10a by a general grindstone and is regulated to a predetermined accuracy. Thereby, strength is ensured by preventing cracking due to fire cracking or impact load, and the fitting surface 12 is prevented from being scratched in the axial direction on the fitting surface 12 by the press-fitting of the cored bar 20. The coaxiality can be obtained, and stable airtightness can be secured over a long period of time.

  Here, when the hardened layers 13 and 14 are formed by induction hardening, in order to prevent heat energy from concentrating on the counter parts 17 and 22 of the outer member 10 from which the heat energy has protruded, resulting in abnormal heating and causing cracks and the like. As shown in FIG. 3, these counter portions 17 and 22 may be eliminated or formed small. The same parts, the same parts, or the parts having the same functions as those of the above-described embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 3 (a), the outer end of the outer member 10 ′ has a groove bottom secured to such an extent that the groove diameter of the outer rolling surface 10a can be easily measured. The fitting surface 11 is formed via the connecting portion 23. Further, as shown in FIG. 3 (b), as in (a), the end on the inner side of the outer member 10 ′ is also smoothly inclined toward the fitting surface 12 from the groove diameter of the outer rolling surface 10a. A connecting portion 24 is formed. Thereby, the quenching part can be smoothed, abnormal heating can be prevented, the range of the hardened layers 13 and 14 can be easily controlled, and a desired quenching pattern can be obtained.

  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 first to fourth generation wheel bearing devices provided with a seal that fits between an outer member and metals.

It is a longitudinal section showing one embodiment of a wheel bearing device concerning the present invention. (A) is a principal part enlarged view which shows the seal | sticker fitting part of the outer side of FIG. (B) is the principal part enlarged view which shows the seal fitting part by the side of an inner side same as the above. (A) is a principal part enlarged view which shows the modification of Fig.2 (a). (B) is a principal part enlarged view which shows the modification of FIG.2 (b). (A) is a longitudinal cross-sectional view which shows the seal | sticker of the conventional wheel bearing apparatus. (B) is the principal part enlarged view of (a).

Explanation of symbols

1 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner member 2 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub wheel 2a, 3a ・ ・ ・ ・ ・ ・ ・ ・···· Inner rolling surface 2b ·········· Small diameter step 2c ············· Serration 3・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 4 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel mounting flange 4a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Base 5・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub Bolt 6 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Retainer 7 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・... Rolling element 8 ... Outer side seal 9 ... Inner side seal 10,10 '·········· Outer member 10a ············ Outside rolling surface 10b Car body mounting flange 10c ... End face 10d on the outer side of the outer member ...・ End surfaces 11 and 12 on the inner side of the outer member... Fitting surfaces 13 and 14... Cured layers 15 and 20. ......... Cores 15a, 18a, 20a ......... Cylindrical part 15b ......... Inner parts 16, 21 ... ······· Seal members 16a, 16b and 21a ··· Side lips 16c, 21b and 21c ··· Radial lips 16d and 21d ··· Projection 17 , 22 ..... Counter part 18 ... Slinger 18b, 20b ... Standing plate part 19・ ・··························· Seal plate 23, 24 ······················ Housing 51a ····································· 53 ... sleeve member 53a ... flange part 53b ... Sleeve part 54 ... Metal ring 54a ... Cylindrical part 54b ... .... Annular part 54c ..... Recessed part 55 ..... Elastic member 55a ... .... Main lip 55b ... Dustrip 5c ... Edge seal A ... Air side O ...・ ・ ・ ・ ・ Sealed fluid side

Claims (5)

An outer member in which a double row outer rolling surface is integrally formed on the inner periphery;
An inner member provided on the outer periphery with a double-row inner rolling surface facing the double-row outer rolling surface;
A double row rolling element group accommodated so as to be freely rollable between the rolling surfaces of the inner member and the outer member via a cage,
In a wheel bearing device comprising a seal mounted in an opening of an annular space formed between the outer member and the inner member,
The seal is formed by pressing a steel plate, and includes a metal core that is a fitting between the outer member and the metal, and a seal member integrally joined to the metal core,
A predetermined hardened layer is formed by induction quenching from the outer rolling surface of the outer member to the fitting surface of the seal, and this hardened layer exceeds the fitting portion of the metal core, and the outer member A wheel bearing device characterized by being stopped in the vicinity of the end face of the wheel.   The counter part of the outer rolling surface is abolished or reduced, and a groove bottom is secured to such an extent that the groove diameter of the outer rolling surface can be easily measured, and a smooth connecting portion is provided between the groove bottom and the fitting surface. The wheel bearing device according to claim 1, wherein:   The core bar has a cylindrical portion that is press-fitted into the fitting surface via a predetermined shimoshiro, and the seal member protrudes outside the outer peripheral surface of the cylindrical portion and covers the exposed portion of the core bar. The wheel bearing device according to claim 1, further comprising a projecting portion joined in such a manner.   The wheel bearing device according to any one of claims 1 to 3, wherein the fitting surface is regulated to a predetermined accuracy by grinding.   The wheel bearing device according to claim 4, wherein the fitting surface is ground simultaneously with the outer rolling surface by a general-purpose grindstone.

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