JP2009250297A - Wheel bearing seal and wheel bearing device provided with the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wheel bearing seal that achieves a longer service lifetime of a bearing by enhancing sealability and durability of a seal, and a wheel bearing device provided with the same. <P>SOLUTION: The wheel bearing device is configured as follows. Each seal 8, 9 is composed of a core metal 19, which includes a cylindrical fitting part 19a press-fitted to the inner periphery of the end part of an external member 5 via a prescribed shrink range and an inner-diameter part 19b extending from the fitting part 19a radially inward, and a seal member 20 integrally joined to the core metal 19 by cure adhesion. An end edge seal part 21 is formed over an area from the outer periphery to the inner-diameter part 19b so as to cover the end part of the core metal 19. The end edge seal part 21 is configured with two annular protruding parts 21a, formed further protrudingly to the outer-diameter side than the outer peripheral face of the fitting part 19a of the core metal 19 and having an almost trapezoidal cross-section, and an annular recessed part 21b formed between the protruding parts 21a. The end edge seal part 21 is elastically suitable for the external member 5 via a prescribed shrink range δ. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a wheel bearing device for rotatably supporting a wheel of an automobile or the like with respect to a suspension device, and more specifically, to improve the sealing performance and durability of a seal mounted on a bearing portion, thereby extending the life of the bearing. The present invention relates to a wheel bearing seal and a wheel bearing device including the same.

  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, the damage due to the sealing failure is a major factor. Therefore, the bearing life can be reliably improved by enhancing the sealing performance and durability of the seal.

  Conventionally, various seals with improved sealing performance have been proposed. A typical example of such a seal is shown in FIG. The seal 50 is attached to a housing (outer member) 51 as two members that are assembled concentrically and relatively rotatably, and a rotary shaft (inner member) 52 inserted into the housing 51. An annular gap between the shaft member 52 and the sleeve member 53 that rotates together with the shaft 52 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. A main lip 55a and a dust lip 55b are continuously fixed to the surface of the side A by an elastic member 55. 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. 4B is an enlarged view of the portion B in FIG. 4A. 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

  However, in such a conventional seal 50, 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, and this protruding portion causes the tapered portion 51a of the opening of the housing 51 to be formed. However, the metal ring 54 that is press-fitted into the housing 51 may be deformed from a single state due to the influence of squeezing. Further, during traveling of the vehicle, a large moment load is applied to the housing 51, and the fitting portion with the metal ring 54 may be deformed. If the edge seal portion 55c of the seal 50 cannot follow such deformation, the sealing performance of the seal 50 may be deteriorated. In particular, when the seal 50 is used in a bearing portion of a wheel bearing device that is exposed to a poor environment, muddy water or the like enters the inside of the bearing from the tapered portion 51a of the opening portion of the housing 51 through the fitting portion. It becomes difficult to ensure a long life.

  The present invention has been made in view of such a conventional problem, and provides a wheel bearing seal and a wheel bearing device including the same, which improve the sealing performance and durability of the seal to extend the life of the bearing. The purpose is to provide.

  In order to achieve such an object, the invention according to claim 1 of the present invention is a cylindrical fitting portion that is press-fitted into the inner periphery of the end portion of the outer member serving as the stationary member via a predetermined shimiro, and It consists of a cored bar consisting of an inner diameter part extending radially inward from this fitting part, and a seal member integrally joined to this cored bar by vulcanization adhesion, from the outer periphery so as to cover the end of the cored bar In the wheel bearing seal in which the edge seal part is formed over the inner diameter part, the edge seal part is formed to protrude to the outer diameter side from the outer peripheral surface of the fitting part of the core metal, and at least It is divided into a plurality of parts by providing convex portions.

  As described above, a core including a cylindrical fitting portion press-fitted to the inner periphery of the end portion of the outer member serving as the fixed side member via a predetermined shimeiro, and an inner diameter portion extending radially inward from the fitting portion. A wheel bearing comprising a gold and a seal member integrally joined to the core metal by vulcanization adhesion, and having an edge seal portion extending from the outer periphery to the inner diameter portion so as to cover the end portion of the core metal In the seal, the edge seal portion is formed so as to protrude to the outer diameter side from the outer peripheral surface of the fitting portion of the core metal, and is divided into a plurality by providing at least a convex portion, so that it is press-fitted into the outer member. Even if the fitting part may be deformed from a single state due to the influence of the core, the large moment load is applied to the outer member while the vehicle is running, and the fitting part with the metal core is deformed. The edge seal part of the seal against such deformations It can follow and prevent muddy water from entering the inside of the bearing from the fitting part with the outer member even when exposed to a bad environment, and improve the seal sealing performance and durability to extend the life of the bearing. An intended wheel bearing seal can be provided.

  Preferably, as in the invention described in claim 2, the edge seal portion is composed of two annular protrusions and an annular recess formed between the protrusions, and the edge. If the seal part is elastically fitted to the outer member via a predetermined squeeze, the filling rate of the edge seal part can be increased compared to the conventional case, and the squeeze of the edge seal part is increased accordingly. Is possible.

  Further, as in the invention described in claim 3, the convex portion may be formed of any one of a substantially trapezoidal shape, a substantially triangular shape and a substantially semicircular shape, or a combination thereof.

  Further, as in the invention described in claim 4, if the squeeze of the convex part on the bearing inner side of the convex part is set smaller than the shimeoshiro of the convex part on the outer side of the bearing, the assemblability is improved. Can be improved.

  Further, as in the invention described in claim 5, if the concave portion is filled with a sealing agent, the airtightness of the fitting portion of the seal can be further improved.

  In addition, if the sealing agent is non-curable as in the invention described in claim 6, it is not necessary to consider the curing time of the sealing agent in a single seal product before assembly, and product management before assembly Can be simplified and the cost can be reduced.

  Further, as in the invention described in claim 7, if the sealing agent is curable, the sealing agent is cured to increase the airtightness and further improve the sealing performance of the fitting portion of the seal.

  Preferably, if the sealant is an anaerobic type as in the invention described in claim 8, unlike the solvent type, the thinning phenomenon that the volume of the solvent evaporated upon solidification does not occur and the sealing agent is sealed. In addition, it is possible to improve the property, and the curing can be performed quickly, and the assemblability can be improved.

  Further, as in the invention according to claim 9 of the present invention, an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and an outer rolling surface facing the double row on the outer periphery. An inner member in which a double row inner rolling surface is formed, and a double row rolling element that is rotatably accommodated between both the inner member and the outer member via a cage. And a seal attached to an opening of an annular space formed between the outer member and the inner member, and at least one of these seals is in any one of claims 1 to 8. With the wheel bearing device comprising the wheel bearing seal that has been made, it is possible to improve the sealing performance and durability of the seal and to prolong the life of the bearing.

  The wheel bearing seal according to the present invention includes a cylindrical fitting portion that is press-fitted into the inner periphery of an end portion of an outer member serving as a fixed-side member via a predetermined shimiro, and radially inward from the fitting portion. An end seal that extends from the outer periphery to the inner diameter portion so as to cover the end portion of the core metal, comprising a core metal having an inner diameter portion that extends and a seal member integrally joined to the core metal by vulcanization adhesion In the wheel bearing seal in which the portion is formed, the edge seal portion is formed to protrude to the outer diameter side from the outer peripheral surface of the fitting portion of the core metal, and is divided into a plurality by providing at least a convex portion. Therefore, even if the core metal pressed into the outer member is deformed from a single state due to the influence of the squeeze, a large moment load is applied to the outer member while the vehicle is running. Even if the fitting part with the metal core is deformed, The seal edge of the seal can follow the deformation, preventing muddy water from entering the inside of the bearing from the fitting part with the outer member even when exposed to a poor environment, and sealing performance of the seal Further, it is possible to provide a wheel bearing seal that enhances durability and extends the life of the bearing.

  An outer member integrally having a vehicle body mounting flange to be attached to the suspension device on the outer periphery, a double row outer rolling surface formed integrally on the inner periphery, and a wheel mounting flange for attaching a wheel to one end And a hub wheel in which one inner rolling surface facing the outer rolling surface of the double row is formed on the outer periphery, and a small-diameter step portion extending in the axial direction from the inner rolling surface, and the hub An inner member formed of an inner ring press-fitted into a small-diameter step portion of the ring and having the other inner rolling surface opposed to the outer rolling surface of the double row on the outer periphery; and the inner member and the outer member A double row rolling element accommodated between the rolling surfaces via a cage, and a seal attached to an opening of an annular space formed between the outer member and the inner ring. A circle in which these seals are press-fitted into the inner periphery of the end portion of the outer member via a predetermined shimoshiro And a seal member integrally joined to the core metal by vulcanization adhesion, and an end of the core metal. In the wheel bearing device in which the edge seal portion is formed from the outer periphery to the inner diameter portion so as to cover the portion, the edge seal portion is on the outer diameter side than the outer peripheral surface of the fitting portion of the cored bar. Are formed of two annular convex portions having a substantially trapezoidal cross section and an annular concave portion formed between the convex portions, and the edge seal portion is formed with respect to the outer member. It is elastically fitted through a predetermined shimoshiro.

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 one seal portion of FIG. 1, and FIG. ) Is an enlarged view showing the edge seal portion of the core metal, and FIGS. 3A to 3G are enlarged views showing a modification of the edge seal portion of 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 called the third generation for driving wheels, and is provided with an inner member 3 composed of a hub wheel 1 and an inner ring 2, and the inner member 3 via double row rolling elements (balls) 4, 4. The outer joint member 11 of the constant velocity universal joint 10 is coupled to the hub wheel 1.

  The hub wheel 1 integrally has a wheel mounting flange 6 for attaching a wheel (not shown) to an end portion on the outer side, one (outer side) inner rolling surface 1a on the outer periphery, and this inner rolling. A cylindrical small diameter step portion 1b extending in the axial direction from the surface 1a is formed, and a serration (or spline) 1c for torque transmission is formed on the inner periphery. Further, hub bolts 6 a are implanted at circumferentially equidistant positions of the wheel mounting flange 6. The inner ring 2 is formed with the other (inner side) inner rolling surface 2a on the outer periphery, and is press-fitted and fixed to the small-diameter step portion 1b of the hub ring 1 through a predetermined shimiro.

  The hub wheel 1 is made of medium and high carbon steel containing carbon of 0.40 to 0.80 wt% such as S53C, and includes a wheel mounting flange 6 serving as a seal land portion of an outer seal 8 to be described later, including the inner rolling surface 1a. The surface is hardened in the range of 54 to 64 HRC by induction hardening from the inner side base 6b to the small diameter step 1b. On the other hand, the inner ring 2 and the rolling element 4 are made of high carbon chrome steel such as SUJ2, and are hardened in a range of 54 to 64 HRC up to the core portion by quenching.

  The outer member 5 integrally has a vehicle body mounting flange 5b to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and the inner rolling surfaces 1a and 2a of the inner member 3 on the inner periphery. Opposing double-row outer rolling surfaces 5a and 5a are integrally formed. Between these rolling surfaces 5a, 1a and 5a, 2a, double-row rolling elements 4, 4 are accommodated via a cage 7 so as to roll freely. The outer member 5 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer raceway surfaces 5a and 5a have a surface in the range of 54 to 64HRC by induction hardening. It has been cured.

  Further, seals 8 and 9 are attached to the opening of the annular space formed between the outer member 5 and the inner member 3, and leakage of the lubricating grease sealed inside the bearing to the outside and from the outside It prevents rainwater and dust from entering the bearing.

  The outer joint member 11 integrally has a shaft portion 13 extending in the axial direction from the shoulder portion 12. A serration 13a that engages with the serration 1c of the hub wheel 1 is formed on the outer periphery of the shaft portion 13, and a male screw is formed at the end of the serration 13a. Then, the shaft portion 13 of the outer joint member 11 is fitted into the hub wheel 1 through the serrations 1c and 13a until the shoulder portion 12 abuts the end surface of the inner ring 2, and the hub wheel is fixed by the fixing nut 14 fastened to the male screw. 1 and the outer joint member 11 are unitized so that torque can be transmitted and detachable.

  The seal 8 on the outer side of the seals 8 and 9 is a core metal 15 press-fitted through a predetermined shimiro to the inner periphery of the outer side end portion of the outer member 5 serving as a fixed side member. It is composed of an integrated seal composed of a joined seal member 16. The core metal 15 is formed by pressing a cold-rolled steel plate (JIS standard SPCC system or the like).

  On the other hand, the seal member 16 is made of synthetic rubber such as nitrile rubber and is integrally joined to the core metal 15 by vulcanization adhesion. The seal member 16 has a pair of side lips 16a and 16b formed to be inclined outward in the radial direction, and a grease lip 16c formed to be inclined inward of the bearing. A base 6b on the inner side of the wheel mounting flange 6 is formed in a curved surface having a circular cross section, and a side lip 16b and a grease lip 16c are slidably contacted with the base 6b with a predetermined squeeze.

  Further, as shown in an enlarged view in FIG. 2A, the inner-side seal 9 is constituted by a so-called pack seal including an annular seal plate 17 and a slinger 18 which are arranged to face each other. The seal plate 17 includes a cored bar 19 attached to the outer member 5 and a seal member 20 integrally joined to the cored bar 19 by vulcanization adhesion. The core 19 is formed by pressing from a steel plate having rust prevention ability such as an austenitic stainless steel plate (JIS standard SUS304, etc.) or a rust-proof cold rolled steel plate (JIS standard SPCC, etc.). A cylindrical fitting portion 19a that is formed in a substantially L-shaped cross section and is press-fitted into the inner periphery of the end portion of the outer member 5 via a predetermined shimiro, and an inner diameter portion that extends radially inward from the fitting portion 19a 19b.

  On the other hand, the seal member 20 is made of a synthetic rubber such as NBR (acrylonitrile-butadiene rubber), and includes a side lip 20a extending obliquely outward in the radial direction, a grease lip 20b and an intermediate lip 20c formed in a bifurcated shape. Have. Here, the end of the fitting portion 19a of the metal core 19 is reduced in diameter, and an edge seal portion 21 joined from the outer periphery to the inner diameter portion 19b is formed so as to cover the end. Thereby, the fitting surface of the outer member 5 and the cored bar 19 can be sealed by the edge seal portion 21, and rainwater, dust, etc. can be prevented from entering the inside of the bearing from the fitting surface. . In addition to NBR, the material of the seal member 20 is excellent in heat resistance and chemical resistance, such as HNBR (hydrogenated acrylonitrile-butadiene rubber) and EPDM (ethylene propylene rubber), which have excellent heat resistance. Examples thereof include ACM (polyacrylic rubber), FKM (fluorine rubber), EPM (ethylene / propylene rubber), and silicon rubber.

  On the other hand, the slinger 18 has a substantially L-shaped cross section, and includes a cylindrical portion 18a that is press-fitted into the outer diameter of the inner ring 2, and a standing plate portion 18b that extends radially outward from the cylindrical portion 18a. The side lip 20a of the seal member 20 is in sliding contact with the upright plate portion 18b, and the grease lip 20b and the intermediate lip 20c are in sliding contact with the cylindrical portion 18a. Further, the standing plate portion 18b of the slinger 18 is opposed to the seal plate 17 through a slight radial clearance to constitute a labyrinth seal 22.

  Here, in this embodiment, as shown in an enlarged view in FIG. 2B, the edge seal portion 21 is formed so as to protrude to the outer diameter side from the outer peripheral surface of the fitting portion 19 a of the core metal 19. It is comprised by the two cyclic | annular convex parts 21a and 21a and the cyclic | annular recessed part 21b formed between these convex parts 21a and 21a. These concavo-convex portions 21b and 21a are formed in a substantially trapezoidal cross section, and are elastically fitted to the outer member 5 via a predetermined shimiro δ. As a result, even if the metal core 19 press-fitted into the outer member 5 may be deformed from a single state due to the influence of the squeeze, a large moment load may be applied to the outer member 5 while the vehicle is running. The edge seal portion 21 of the seal 9 can follow such deformation even if the fitting portion with the core metal 19 is deformed, and the filling rate of the edge seal portion 21 is higher than that of the conventional case. Therefore, it is possible to increase the size of the edge seal portion 21 by a corresponding amount. Accordingly, even when exposed to a poor environment, muddy water or the like is prevented from entering the inside of the bearing from the fitting portion with the outer member 5, and the seal 9 is improved in sealing performance and durability, thereby extending the life of the bearing. It is possible to provide a wheel bearing device that achieves the above.

  In the present embodiment, the edge seal 21 portion is exemplified by two annular convex portions 21a and 21a and an annular concave portion 21b formed between the convex portions 21a and 21a. For example, although not illustrated, a plurality of protrusions and recesses may be provided, or the protrusions may be divided only by the plurality of protrusions.

  Moreover, as the edge seal part 21, various structures as shown in FIG. 3 can be illustrated. The edge seal portion 23 shown in (a) has two annular convex portions 23a and 23a each having a substantially triangular cross section formed so as to protrude from the outer peripheral surface of the fitting portion 19a of the metal core 19 to the outer diameter side, It is comprised with the cyclic | annular recessed part 23b formed between these convex parts 23a and 23a. And the cross section of the convex parts 23a and 23a is formed in a substantially triangular shape, and the cross section of the recessed part 23b is formed in a substantially trapezoid shape.

  Moreover, the edge seal part 24 of (b) is comprised by the two convex parts 23a and 23a whose cross section is substantially triangular, and the recessed part 24a whose cross section is substantially trapezoid. Since these edge seal portions 23 and 24 have convex portions 23a and 23a formed in a substantially triangular cross section, the amount of deformation when fitted to an outer member (not shown) can be increased. Therefore, a large size can be set compared with the substantially trapezoidal shape, and the sealing performance can be improved.

  The edge seal portion 25 shown in (c) is composed of two convex portions 25a and 25a having a substantially semicircular cross section and a concave portion 25b having a substantially trapezoidal cross section. Further, the edge seal portion 26 shown in (d) is composed of two convex portions 25a and 25a having a substantially semicircular cross section, and a concave portion 26b having a substantially arcuate cross section with a smooth corner portion. Yes. Since these edge seal portions 25 and 26 are formed with the convex portions 25a and 25a having a substantially semicircular cross section, it is possible to prevent the convex portions 25a from being lost at the time of fitting and to improve the assemblability. .

  The edge seal portion 27 shown in (e) includes a convex portion 25a having a substantially semicircular cross section, a convex portion 21a having a substantially trapezoidal cross section, and a concave portion 27a having a substantially trapezoidal cross section. Thereby, assembly property can be improved, ensuring sealing performance. Further, the edge seal portion 28 shown in (f) includes a convex portion 28a having a substantially trapezoidal cross section, a convex portion 21a having a substantially trapezoidal cross section, and a concave portion 28b having a substantially trapezoidal cross section. Although the configuration is basically the same as that of the edge seal portion 21 of b), the outer side convex portion 28a is set smaller than the inner side convex portion 21a. Thereby, assembly property can be improved rather than the edge seal part 21 shown in FIG.2 (b).

  The edge seal portion 29 shown in (g) is composed of two convex portions 28a, 28a having a substantially trapezoidal cross section and a concave portion 29a having a substantially trapezoidal cross section. The edge seal portion shown in FIG. Although the configuration itself is the same as 21, the size is set small. And the recessed part 29a is filled with the sealing compound.

  Sealing agents are made of synthetic rubber, acrylic or ester resins, and can be broadly classified into curable and non-curable. In the case of non-hardening, it is not necessary to consider the curing time of the sealant in a single seal before assembly, and product management before assembly can be simplified and cost can be reduced. On the other hand, in the case of a curable material, the sealing agent is cured, so that the airtightness is increased and the sealing performance of the seal is improved.

  Moreover, there exist a solvent type, an anaerobic type, etc. in sclerosis | hardenability. The solvent type dissolves the polymer resin in the solvent, and the curing is returned to the original resin by evaporating the solvent, so-called solidification, but the anaerobic type does not contain the solvent component and polymerizes by chemical reaction And is cured. Therefore, this anaerobic type does not cause a thinning phenomenon in which the volume of the solvent evaporated upon solidification does not occur, it is possible to improve the sealing performance, and the curing is carried out quickly. Assemblability can be improved as compared with the edge seal portion 21 shown in b).

  Here, the inner side seal 9 made of a composite pack seal has been described. However, the outer side integral seal in which the edge seal portion is joined so as to cover the end portion of the fitting portion of the cored bar. 8 also has the same configuration.

  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 generation to a fourth generation structure in which a seal is attached to an opening of an annular space.

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 one seal | sticker part of FIG. (B) is an enlarged view which shows the edge seal part of the metal core of (a). (A)-(g) is an enlarged view which shows the modification of the edge seal part of FIG.2 (b). (A) is a half sectional view of a conventional seal. (B) is an enlarged view which shows the B section of (a).

Explanation of symbols

1 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub wheel 1a, 2a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner rolling surface 1b ・ ・ ・ ・ ・ ・.... Small diameter step 1c, 13a ... Serration 2 ... Inner ring 3 ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner member 4 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Rolling element 5 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer member 5a・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer rolling surface 5b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Car body mounting flange 6 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ ・ ・ ・ ・ Wheel mounting flange 6a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub bolt 6b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Base 7 ・ ・ ・ ・ ・ ・··························································· Outer seal 9・ ・ ・ ・ ・ ・ ・ ・ ・ Seal 10 on the inner side ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Constant velocity universal joint 11 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outside Joint member 12 ... shoulder 13 ... shaft 14 ...・ ・ ・ ・ Fixing nuts 15 and 19 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Cores 16 and 20 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Seal members 16a, 16b and 20a・ Side lips 16c, 20b ・ ・ ・ ・ ・ ・ Grease lip 17 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Seal plate 18 ・ ・ ・ ・ ・ ・ ・ ・· · Slinger 18a · · · · · · · cylindrical portion 18b · · · · · · · · Standing plate portion 19 ···・ ・ ・ ・ Core 19a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Fitting 19b ·············································· Intermediate lip 21, 23, 24, 25, 26, 27, 28, 29・ Edge seal portions 21a, 23a, 25a, 28a... Convex portions 21b, 23b, 24a, 25b, 26a, 27a, 28b, 29a,. ... Labyrinth seal 50 ... Seal 51 ... Housing 51a ... ... Taper part 52 ... Rotating shaft 53 ... Sleeve member 53a ... ... flange part 53b ... sleeve part 54 ... metal ring 54a ... ·························································· · ..... Elastic member 55a ... Main lip 55b ... Dustrip 55c ...・ ・ ・ ・ ・ ・ ・ ・ Edge seal part A ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Air side O ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ ・ ・ Sealed fluid side δ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Shimeshiro

Claims (9)

A cylindrical fitting portion that is press-fitted through a predetermined shimeshiro to the inner periphery of the end portion of the outer member serving as the fixed side member, and a cored bar that includes an inner diameter portion extending radially inward from the fitting portion;
It consists of a sealing member integrally joined to this mandrel by vulcanization adhesion,
In the wheel bearing seal in which the edge seal portion is formed from the outer periphery to the inner diameter portion so as to cover the end portion of the core metal,
The bearing seal for a wheel, wherein the edge seal portion is formed so as to protrude to the outer diameter side from the outer peripheral surface of the fitting portion of the metal core, and is divided into a plurality of portions by providing at least a convex portion. .   The edge seal portion is composed of two annular protrusions and an annular recess formed between the protrusions, and the edge seal portion provides a predetermined squeeze to the outer member. The wheel bearing seal according to claim 1, wherein the wheel bearing seal is elastically fitted through the wheel.   The wheel bearing seal according to claim 1, wherein the convex portion is configured by any one of a substantially trapezoidal shape, a substantially triangular shape, a substantially semicircular shape, or a combination thereof.   The wheel bearing seal according to any one of claims 1 to 3, wherein a squeeze of a convex part on a bearing inner side of the convex part is set to be smaller than a squeeze of a convex part on a bearing outer side.   The wheel bearing seal according to claim 1, wherein the recess is filled with a sealant.   The wheel bearing seal according to claim 5, wherein the sealant is non-curable.   The wheel bearing seal according to claim 5, wherein the sealant is curable.   The wheel bearing seal according to claim 7, wherein the sealant is an anaerobic type. 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 rolling surfaces of the inner member and the outer member so as to be freely rollable via a cage;
A seal attached to an opening of an annular space formed between the outer member and the inner member;
A wheel bearing device, wherein at least one of the seals comprises the wheel bearing seal according to any one of claims 1 to 8.

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