JP6262548B2 - Sealing device - Google Patents

Sealing device Download PDF

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Publication number
JP6262548B2
JP6262548B2 JP2014010302A JP2014010302A JP6262548B2 JP 6262548 B2 JP6262548 B2 JP 6262548B2 JP 2014010302 A JP2014010302 A JP 2014010302A JP 2014010302 A JP2014010302 A JP 2014010302A JP 6262548 B2 JP6262548 B2 JP 6262548B2
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outer ring
annular
flange
axial end
sealing device
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JP2015137724A (en
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真太郎 境
真太郎 境
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Koyo Sealing Techno Co Ltd
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Koyo Sealing Techno Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Description

本発明は、車輪用転がり軸受装置が備えている内軸と外輪との間の環状空間に装着され、この環状空間に泥水が浸入するのを防ぐ密封装置に関する。   The present invention relates to a sealing device that is mounted in an annular space between an inner shaft and an outer ring provided in a rolling bearing device for a wheel and prevents muddy water from entering the annular space.

自動車等の車両に搭載され、車輪を回転可能に支持する車輪用転がり軸受装置は、同心状に配置された内軸と外輪とを備えており、これら内軸と外輪との間に介在する転動体（玉やテーパローラ）によって、例えば、外輪に対して内軸が回転可能となる。内軸の軸方向車両外側の端部には、径外方向へ延びるフランジが設けられており、このフランジに車輪及びブレーキディスクが取り付けられる。
このような車輪用転がり軸受装置では、内軸と外輪との間に形成され、転動体が配設されている環状空間に泥水が浸入するのを防ぐために、この環状空間の軸方向両端部に密封装置が装着されている。 A rolling bearing device for a wheel mounted on a vehicle such as an automobile and rotatably supporting a wheel includes an inner shaft and an outer ring arranged concentrically, and a rolling intervening between the inner shaft and the outer ring. For example, the inner shaft can rotate with respect to the outer ring by the moving body (ball or taper roller). A flange extending radially outward is provided at an end of the inner shaft on the outer side in the axial direction vehicle, and a wheel and a brake disk are attached to the flange.
In such a rolling bearing device for a wheel, in order to prevent muddy water from entering the annular space formed between the inner shaft and the outer ring and in which the rolling elements are disposed, both axial ends of the annular space are provided. A sealing device is installed.

図３に示すように、環状空間１０９の軸方向車両外側の端部に装着されている密封装置１１０として、外輪１０２に嵌合している芯金１１１と、この芯金１１１に固定されているシール部材１１２とを備えたものがある。
図示例では、芯金１１１は、外輪１０２の端部内周面１２１に嵌合して当該外輪１０２に固定される円筒部１１６、及び当該円筒部１１６から径外方向へ直線的に延びて一部が外輪１０２の軸方向端面１２０に接触する外円環部１１７を有している。
また、シール部材１１２は、弾性部材からなり、外輪１０２、及び外円環部１１７に固定されている外固定部１３５よりも径方向外側において、当該外固定部１３５から軸方向に延びる円筒状のデフレクタ１４０を有している。 As shown in FIG. 3, as a sealing device 110 attached to the outer end of the annular space 109 in the axial direction vehicle, a cored bar 111 fitted to the outer ring 102 and the cored bar 111 are fixed. Some include a seal member 112.
In the illustrated example, the core metal 111 is fitted to the inner peripheral surface 121 of the end portion of the outer ring 102 and is fixed to the outer ring 102, and a part extending linearly from the cylindrical portion 116 radially outward. Has an outer ring portion 117 that contacts the axial end surface 120 of the outer ring 102.
The seal member 112 is made of an elastic member, and has a cylindrical shape extending in the axial direction from the outer fixing portion 135 on the outer side in the radial direction from the outer ring 102 and the outer fixing portion 135 fixed to the outer ring portion 117. A deflector 140 is provided.

デフレクタ１４０は、軸方向においてフランジ１０８の側面１２８に近づく方向（車両外側方向）へ延びて当該側面１２８に所定間隔を隔てて対向する環状突部１４１を備えている。環状突部１４１は、当該環状突部１４１の軸方向端部１４１ｅの内周縁１４１ｆのみがフランジ１０８の角部１２９ｂ付近において側面１２８と近接するように配設されている。また、環状突部１４１の内周縁１４１ｆとフランジ１０８の側面１２８との軸方向の隙間ｓ１の寸法は通常１．０±０．５ｍｍに設定されている。   The deflector 140 includes an annular protrusion 141 that extends in a direction approaching the side surface 128 of the flange 108 in the axial direction (vehicle outward direction) and faces the side surface 128 with a predetermined interval therebetween. The annular protrusion 141 is disposed so that only the inner peripheral edge 141 f of the axial end 141 e of the annular protrusion 141 is close to the side surface 128 in the vicinity of the corner 129 b of the flange 108. The dimension of the axial gap s1 between the inner peripheral edge 141f of the annular protrusion 141 and the side surface 128 of the flange 108 is normally set to 1.0 ± 0.5 mm.

上述の密封装置１１０によれば、軸方向端部１４１ｅの内周縁１４１ｆと側面１２８との軸方向の隙間ｓ１の寸法が１．０±０．５ｍｍに設定されていることで、高速回転（例えば１０００ｒｐｍ）時において、軸方向端部１４１ｅの内周縁１４１ｆと、フランジ１０８の側面１２８における前記内周縁１４１ｆに対向する部分との間に表面張力による泥水ｗの膜が形成される。密封装置１１０は、この泥水ｗの膜の形成により、泥水ｗが内リップ部１３１，１３２，１３３側へ浸入することを抑制している。これにより、泥水ｗが内リップ部１３１，１３２，１３３近傍で滞留して内軸１０３の内リップ部摺動部分が錆びることを防止できる。その結果、内リップ部１３１，１３２，１３３が錆びにより摩耗して不具合が発生することを回避できる。   According to the sealing device 110 described above, the dimension of the axial gap s1 between the inner peripheral edge 141f of the axial end portion 141e and the side surface 128 is set to 1.0 ± 0.5 mm. 1000 rpm), a film of muddy water w due to surface tension is formed between the inner peripheral edge 141f of the axial end portion 141e and the portion of the side surface 128 of the flange 108 facing the inner peripheral edge 141f. The sealing device 110 suppresses the intrusion of the muddy water w into the inner lip portions 131, 132, and 133 by the formation of the muddy water w film. Thereby, it is possible to prevent the muddy water w from staying in the vicinity of the inner lip portions 131, 132, 133 and rusting the sliding portion of the inner lip portion of the inner shaft 103. As a result, it can be avoided that the inner lip portions 131, 132, 133 are worn due to rust and a malfunction occurs.

しかし、前記密封装置１１０では、軸方向端部１４１ｅの内周縁１４１ｆとフランジ１０８の側面１２８との間に泥水ｗを十分量保持できないために、泥水ｗが内リップ部１３１，１３２，１３３側へ浸入する虞があった。
本発明は、このような事情に鑑みてなされたものであり、外部から内リップ部側への泥水の浸入を防止して耐泥水性能を向上させた密封装置を提供することを目的とする。 However, in the sealing device 110, since a sufficient amount of muddy water w cannot be held between the inner peripheral edge 141f of the axial end portion 141e and the side surface 128 of the flange 108, the muddy water w moves toward the inner lip portions 131, 132, 133. There was a risk of intrusion.
This invention is made | formed in view of such a situation, and it aims at providing the sealing device which prevented the intrusion of the muddy water from the outside to the inner lip part side, and improved the muddy water resistance.

上記目的を達成する本発明は、同心状に配置された内軸と外輪とを備え、当該外輪の軸方向端面に間隔を隔てて対向する側面を有したフランジが前記内軸の端部に設けられた車輪用転がり軸受装置に用いられ、前記内軸と前記外輪との間の環状空間に泥水が浸入するのを防ぐ密封装置であって、
前記外輪の端部内周面に嵌合して当該外輪に固定される円筒部、及び当該円筒部から径方向外方へ延びて前記外輪の軸方向端面に当接する外円環部を有する芯金と、
前記内軸に設けられているシール面に摺接する内リップ部、及び前記内リップ部の径方向外方で前記フランジの側面に近づく側に延びて当該側面に対向する環状突部を有するシール部材と、を備え、
前記環状突部の軸方向端部は、表面張力により泥水の膜が生じ得る隙間を隔てて前記フランジの側面と対向しており、且つ環状溝を有しており、
前記環状溝が、前記環状突部と前記フランジの側面とが対向している径方向の領域よりも径方向外側に位置していることを特徴とする。
The present invention that achieves the above object includes an inner shaft and an outer ring arranged concentrically, and a flange having a side surface facing the axial end surface of the outer ring with a gap is provided at an end of the inner shaft. A sealing device that is used in a rolling bearing device for a wheel that prevents muddy water from entering the annular space between the inner shaft and the outer ring,
A metal core having a cylindrical portion that is fitted to the inner peripheral surface of the end portion of the outer ring and is fixed to the outer ring, and an outer annular portion that extends radially outward from the cylindrical portion and contacts the axial end surface of the outer ring. When,
A seal member having an inner lip portion slidably in contact with a seal surface provided on the inner shaft, and an annular protrusion that extends radially outward of the inner lip portion toward the side of the flange and faces the side surface And comprising
The axial end of the annular protrusion is opposed to the side surface of the flange with a gap in which a muddy water film may be generated by surface tension, and has an annular groove .
The annular groove is located on a radially outer side than a radial region where the annular protrusion and the side surface of the flange face each other.

本発明の密封装置によれば、フランジの側面と環状突部の軸方向端部との間に表面張力による泥水の膜が生じ得る。また、本発明の密封装置は、シール部材の環状突部の軸方向端部に環状溝を有しており、この環状溝に泥水を表面張力によって付着させて保持させることができる。このため、本発明の密封装置は、環状溝を有しない従来のものよりも環状突部の軸方向端部とフランジの側面の間の泥水保持機能を向上させることができる。これにより、本発明の密封装置は、外部から内リップ部側への泥水の浸入を抑えて耐泥水性能を向上させることができる。   According to the sealing device of the present invention, a muddy water film can be generated between the side surface of the flange and the axial end of the annular protrusion due to surface tension. Further, the sealing device of the present invention has an annular groove at the axial end of the annular protrusion of the seal member, and mud can be attached to the annular groove by surface tension and held. For this reason, the sealing device of this invention can improve the muddy water holding | maintenance function between the axial direction edge part of an annular protrusion, and the side surface of a flange rather than the conventional thing which does not have an annular groove. Thereby, the sealing device of the present invention can improve the muddy water resistance performance by suppressing the intrusion of muddy water from the outside to the inner lip portion side.

本発明の密封装置によれば、外部から内リップ部側への泥水の浸入を防止して耐泥水性能を向上させることができる。   According to the sealing device of the present invention, muddy water can be prevented from entering from the outside to the inner lip portion side, and the muddy water resistance can be improved.

本発明の一実施形態に係る密封装置が装着されている車輪用転がり軸受装置の断面説明図である。It is a section explanatory view of the rolling bearing device for wheels with which the sealing device concerning one embodiment of the present invention is equipped. 本発明の一実施形態に係る密封装置の断面説明図である。It is a section explanatory view of the sealing device concerning one embodiment of the present invention. 従来の密封装置の断面説明図である。It is sectional explanatory drawing of the conventional sealing device.

以下、本発明の実施形態を図面に基づいて説明する。
図１は、本発明の一実施形態に係る密封装置１０が用いられている車輪用転がり軸受装置１を示す断面説明図である。また、図２は、図１における密封装置１０の断面説明図である。図２では、外輪２及び内軸３（フランジ８及び軸本体部６）を二点鎖線で示している。車輪用転がり軸受装置１（以下、単に「軸受装置」ともいう。）は、自動車の車体に設けられている懸架装置５０に対して車輪を回転可能に支持するためのものであり、図１に示すように、外輪２と内軸３とを備えている。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional explanatory view showing a wheel rolling bearing device 1 in which a sealing device 10 according to an embodiment of the present invention is used. 2 is a cross-sectional explanatory view of the sealing device 10 in FIG. In FIG. 2, the outer ring 2 and the inner shaft 3 (the flange 8 and the shaft main body portion 6) are indicated by a two-dot chain line. A wheel rolling bearing device 1 (hereinafter also simply referred to as a “bearing device”) is for rotatably supporting a wheel with respect to a suspension device 50 provided on a vehicle body of an automobile. As shown, an outer ring 2 and an inner shaft 3 are provided.

外輪２は円筒形状の部材であり、車体側の懸架装置５０に固定される。
内軸３は、軸本体部６と、この軸本体部６の車両内側Ａ１の端部に外嵌して固定されている環状の内輪部材７とを有している。外輪２と内軸３との間には２列で且つ各列に複数の玉４が介在している。外輪２と内軸３とは同心状に配置され、本実施形態では、外輪２に対して内軸３が回転自在となっている。また、この軸受装置１は、複数の玉４を保持する保持器５を備えている。 The outer ring 2 is a cylindrical member and is fixed to the suspension device 50 on the vehicle body side.
The inner shaft 3 includes a shaft main body portion 6 and an annular inner ring member 7 that is fitted and fixed to an end portion of the shaft main body portion 6 on the vehicle inner side A1. There are two rows between the outer ring 2 and the inner shaft 3, and a plurality of balls 4 are interposed in each row. The outer ring 2 and the inner shaft 3 are arranged concentrically. In the present embodiment, the inner shaft 3 is rotatable with respect to the outer ring 2. The bearing device 1 also includes a cage 5 that holds a plurality of balls 4.

内軸３の車両外側Ａ２の端部には、車輪及びブレーキディスク（図示せず）を取り付けるためのフランジ８が設けられている。このフランジ８が有する車両内側Ａ１の側面２８の一部は、外輪２の軸方向端面２０と、間隔Ｓを隔てて対向している。
以上の構成により、軸受装置１は、複列のアンギュラ玉軸受を構成し、図示しない車輪及びブレーキディスクがフランジ８に固定された内軸３を、車両に対して回転可能に支持することができる。 A flange 8 for attaching a wheel and a brake disk (not shown) is provided at the end of the inner shaft 3 on the vehicle outer side A2. A part of the side surface 28 of the vehicle inner side A <b> 1 included in the flange 8 faces the axial end surface 20 of the outer ring 2 with an interval S therebetween.
With the above configuration, the bearing device 1 constitutes a double-row angular ball bearing, and can support the inner shaft 3 in which a wheel and a brake disk (not shown) are fixed to the flange 8 so as to be rotatable with respect to the vehicle. .

フランジ８の側面２８は、図２に示すように、第１側面２８ａと第２側面２８ｂと第３側面２８ｃとを有している。第１側面２８ａは、軸本体部６の外周面６ａと滑らかに連続している。第２側面２８ｂは、第１側面２８ａの径外方向において第１側面２８ａよりも軸方向車両外側Ａ２に設けられている。第３側面２８ｃは、第２側面２８ｂの径外方向において第２側面２８ｂよりもさらに軸方向車両外側Ａ２に設けられている。第１側面２８ａと第２側面２８ｂとの間には鈍角の第１角部２９ａが形成されており、第２側面２８ｂと第３側面２８ｃとの間には略直角の第２角部２９ｂが形成されている。第１側面２８ａは第１角部２９ａに至るまで滑らかに連続しており、第２側面２８ｂは第１角部２９ａから第２角部２９ｂに至るまで滑らかに連続している。また、フランジ８の側面２８は第２側面２８ｂと第３側面２８ｃとの間に外周面２８ｄを有しており、外周面２８ｄと第３側面２８ｃとは滑らかに連続している。   As shown in FIG. 2, the side surface 28 of the flange 8 includes a first side surface 28a, a second side surface 28b, and a third side surface 28c. The first side surface 28 a is smoothly continuous with the outer peripheral surface 6 a of the shaft main body 6. The second side surface 28b is provided on the outer side A2 in the axial direction than the first side surface 28a in the radially outward direction of the first side surface 28a. The third side surface 28c is provided further on the outer side A2 in the axial direction than the second side surface 28b in the radially outward direction of the second side surface 28b. An obtuse angled first corner portion 29a is formed between the first side surface 28a and the second side surface 28b, and a substantially right angle second corner portion 29b is formed between the second side surface 28b and the third side surface 28c. Is formed. The first side surface 28a continues smoothly until reaching the first corner portion 29a, and the second side surface 28b continues smoothly from the first corner portion 29a to the second corner portion 29b. Further, the side surface 28 of the flange 8 has an outer peripheral surface 28d between the second side surface 28b and the third side surface 28c, and the outer peripheral surface 28d and the third side surface 28c are smoothly continuous.

図１に示すように、外輪２の軸方向両端部と内軸３との間には、密封装置１０，６０が取り付けられている。これら密封装置１０，６０は、外輪２の径方向外側から外輪２と内軸３との間に形成される環状空間９に泥水ｗが浸入するのを防ぐ役割を有する。そして、これら密封装置１０，６０のうち、車両外側Ａ２の密封装置１０が本発明の一実施形態に係る密封装置１０である。
この密封装置１０は、図２に示すように、外輪２の軸方向一端部に固定されている円環状の芯金１１と、この芯金１１に取り付けられたシール部材１２とを備えている。 As shown in FIG. 1, sealing devices 10 and 60 are attached between the axial ends of the outer ring 2 and the inner shaft 3. These sealing devices 10 and 60 have a role of preventing the muddy water w from entering the annular space 9 formed between the outer ring 2 and the inner shaft 3 from the outer side in the radial direction of the outer ring 2. And among these sealing devices 10 and 60, the sealing device 10 of vehicle outer side A2 is the sealing device 10 which concerns on one Embodiment of this invention.
As shown in FIG. 2, the sealing device 10 includes an annular core metal 11 fixed to one axial end of the outer ring 2 and a seal member 12 attached to the core metal 11.

芯金１１は、ＳＰＣＣ等の鋼板をプレス加工することによって環状に形成されている。芯金１１は、外輪２の端部内周面２１に嵌合して外輪２に固定されている円筒部１６と、この円筒部１６の軸方向車両外側Ａ２の端部から径外方向へ延びて外輪２の軸方向端面２０に当接する外円環部１７とを有している。また、芯金１１は、円筒部１６の軸方向車両内側Ａ１の端部に連続する屈曲部１８と、この屈曲部１８から径内方向へ延びる内円環部１９とを有している。   The core metal 11 is formed in an annular shape by pressing a steel plate such as SPCC. The core metal 11 extends radially outward from the cylindrical portion 16 that is fitted to the end inner peripheral surface 21 of the outer ring 2 and is fixed to the outer ring 2, and the end of the cylindrical portion 16 on the outer side A2 in the axial direction of the vehicle. The outer ring portion 17 is in contact with the axial end surface 20 of the outer ring 2. The metal core 11 has a bent portion 18 that is continuous with the end portion of the cylindrical portion 16 on the inner side A1 in the axial direction, and an inner annular portion 19 that extends radially inward from the bent portion 18.

外円環部１７は、その先端部１７ｅに至るまで径外方向へ直線的に延びている。先端部１７ｅは、外輪２の端部外周面２２ａ及び後述するデフレクタ４０の外リップ部４５の基端部内周面４９よりも径方向外側、且つ、デフレクタ４０の内部に位置している。
外円環部１７は、外輪２の軸方向端面２０に当接することで、密封装置１０全体を軸方向に関して位置決めする。また、外円環部１７は、外輪２の軸方向端面２０に当接した状態で、フランジ８の第２側面２８ｂと、シール部材１２の一部（後述の外固定部３５）を挟んで対向するように配置されている。 The outer ring portion 17 extends linearly outward in the radial direction until reaching the tip portion 17e. The distal end portion 17e is located on the radially outer side of the end outer peripheral surface 22a of the outer ring 2 and the base end inner peripheral surface 49 of the outer lip portion 45 of the deflector 40, which will be described later, and inside the deflector 40.
The outer annular portion 17 contacts the axial end surface 20 of the outer ring 2 to position the entire sealing device 10 in the axial direction. The outer annular portion 17 is opposed to the second side surface 28b of the flange 8 with a part of the seal member 12 (an outer fixing portion 35 described later) sandwiched between the outer ring 2 and the axial end surface 20 of the outer ring 2. Are arranged to be.

外円環部１７は、外輪２の軸方向端面２０に接触している当接部１７ａと、この当接部１７ａが軸方向端面２０に接触した状態で当該軸方向端面２０に非接触となる非当接部１７ｂとを有している。当接部１７ａは外円環部１７の基端側（径方向内側）を構成し、非当接部１７ｂは外円環部１７の先端側（径方向外側）を構成している。非当接部１７ｂは当接部１７ａに比べて厚さ（軸方向寸法）が薄くなっており、外円環部１７のフランジ８側の面は平坦であるが外円環部１７の外輪２側の面は段部を有している。   The outer ring portion 17 is in contact with the axial end surface 20 in a state where the abutting portion 17a is in contact with the axial end surface 20 of the outer ring 2 and the abutting portion 17a is in contact with the axial end surface 20. And a non-contact portion 17b. The abutting portion 17a constitutes the proximal end side (radially inner side) of the outer annular portion 17, and the non-abutting portion 17b constitutes the distal end side (radially outer side) of the outer annular portion 17. The non-contact portion 17b has a smaller thickness (axial dimension) than the contact portion 17a, and the surface of the outer ring portion 17 on the flange 8 side is flat, but the outer ring 2 of the outer ring portion 17 is flat. The side surface has a step.

シール部材１２は、ニトリルゴム等のゴムを円環状に形成したものであり、芯金１１に加硫接着している。シール部材１２のゴムの硬度は、ＪＩＳ−Ｋ６２５３に基づきデュロメータタイプＡにより２３℃の環境下で測定したデュロメータＡ硬さで、例えば７０〜８０度のものが用いられている。シール部材１２は、第１シール部１３と第２シール部１４とで構成されている。第１シール部１３は、芯金１１の円筒部１６、屈曲部１８及び内円環部１９に固定されている部分であり、第２シール部１４は、芯金１１の外円環部１７に固定されている部分及びその径方向外側の部分である。なお、本実施形態では、第１シール部１３と第２シール部１４とは一体形成されている。   The seal member 12 is made of rubber such as nitrile rubber in an annular shape, and is vulcanized and bonded to the core metal 11. The hardness of the rubber of the seal member 12 is a durometer A hardness measured in a 23 ° C. environment with a durometer type A based on JIS-K6253, for example, 70 to 80 degrees. The seal member 12 includes a first seal portion 13 and a second seal portion 14. The first seal portion 13 is a portion fixed to the cylindrical portion 16, the bent portion 18 and the inner annular portion 19 of the core metal 11, and the second seal portion 14 is attached to the outer annular portion 17 of the core metal 11. These are the fixed part and the radially outer part. In the present embodiment, the first seal portion 13 and the second seal portion 14 are integrally formed.

第１シール部１３は、芯金１１の円筒部１６、屈曲部１８及び内円環部１９に固定されている内固定部３０と、この内固定部３０から内軸３へ向かって延びている内リップ部３１，３２，３３とを有している。そして、内リップ部３１，３２，３３は、内軸３に設けられているシール面に摺接する。   The first seal portion 13 extends to the inner shaft 3 from the inner fixed portion 30 fixed to the cylindrical portion 16, the bent portion 18 and the inner ring portion 19 of the core metal 11. Inner lip portions 31, 32, 33 are provided. The inner lip portions 31, 32, 33 are in sliding contact with the seal surface provided on the inner shaft 3.

本実施形態では、第１の内リップ部３１が摺接するシール面は、フランジ８の側面２８（第１側面２８ａ）であり、第２の内リップ部３２及び第３の内リップ部３３が摺接するシール面は、軸本体部６の外周面６ａである。これら内リップ部３１，３２，３３は、外輪２の径外方向（つまり、外部）の泥水、砂、小石等の異物が浸入するのを防止する機能、及び環状空間９に設けられている玉４用の潤滑剤が外部へ漏れるのを防止する機能を有している。   In the present embodiment, the seal surface with which the first inner lip portion 31 is in sliding contact is the side surface 28 (first side surface 28a) of the flange 8, and the second inner lip portion 32 and the third inner lip portion 33 are slid. The sealing surface that comes into contact is the outer peripheral surface 6 a of the shaft body 6. These inner lip portions 31, 32, and 33 have a function of preventing foreign matters such as muddy water, sand, and pebbles in the radially outward direction (that is, the outside) of the outer ring 2, and balls provided in the annular space 9. 4 has a function of preventing the lubricant for 4 from leaking to the outside.

第２シール部１４は、芯金１１の外円環部１７に固定されている外固定部３５と、この外固定部３５と一体であるデフレクタ４０とを有している。
外固定部３５は、外円環部１７（当接部１７ａ及び非当接部１７ｂ）よりもフランジ８側の本体部３５ａ、及び非当接部１７ｂと軸方向端面２０の間の第１密封部３５ｂを有している。第１密封部３５ｂは、芯金１１の当接部１７ａよりも軸方向において外輪２側に突出した環状の凸部３５ｂ−１と、当接部１７ａの当接面よりも軸方向においてフランジ８側に凹んでいる環状の凹部３５ｂ−２，３５ｂ−３とを有している。凹部３５ｂ−２，３５ｂ−３は、凸部３５ｂ−１の径方向外側及び内側にそれぞれ配設されている。
芯金１１の当接部１７ａが軸方向端面２０に当接した状態で、凸部３５ｂ−１は、押圧されて軸方向端面２０と密着する。凹部３５ｂ−２，３５ｂ−３は、凸部３５ｂ−１の押圧による非圧縮変形を妨げない機能を有する。 The second seal portion 14 includes an outer fixing portion 35 that is fixed to the outer ring portion 17 of the core metal 11 and a deflector 40 that is integral with the outer fixing portion 35.
The outer fixing portion 35 is a first seal between the body portion 35a on the flange 8 side of the outer ring portion 17 (the contact portion 17a and the non-contact portion 17b), and the non-contact portion 17b and the axial end surface 20. It has a part 35b. The first sealing portion 35b includes an annular convex portion 35b-1 protruding toward the outer ring 2 in the axial direction from the contact portion 17a of the core metal 11, and the flange 8 in the axial direction from the contact surface of the contact portion 17a. It has annular recesses 35b-2 and 35b-3 that are recessed to the side. The concave portions 35b-2 and 35b-3 are respectively disposed on the radially outer side and the inner side of the convex portion 35b-1.
In a state where the contact portion 17 a of the core metal 11 is in contact with the axial end surface 20, the convex portion 35 b-1 is pressed and closely contacts the axial end surface 20. The recesses 35b-2 and 35b-3 have a function that does not hinder uncompressed deformation caused by pressing of the projection 35b-1.

デフレクタ４０は、外固定部３５の径方向外側の端部からフランジ８の側面２８に近づく側へ軸方向に沿って延びる環状突部４１と、外固定部３５の径方向外側の端部からフランジ８の側面２８と離れる側へ軸方向に沿って延びる外リップ部４５とで構成されている。デフレクタ４０は、１．０ｍｍ程度の厚さを有する円筒状に形成されている。   The deflector 40 includes an annular protrusion 41 that extends along the axial direction from the radially outer end of the outer fixing portion 35 toward the side closer to the side surface 28 of the flange 8, and a flange from the radially outer end of the outer fixing portion 35. 8, and an outer lip portion 45 extending in the axial direction toward the side away from the side surface 28. The deflector 40 is formed in a cylindrical shape having a thickness of about 1.0 mm.

環状突部４１の軸方向端部４１ｅは、フランジ８の側面２８と隙間ｓ１を隔てて対向している。軸方向端部４１ｅの内周縁４１ｆは、図２に示すように、フランジ８の側面２８の第２角部２９ｂよりもやや径方向内側に位置しており、軸方向端部４１ｅの内周縁４１ｆのみが当該第２側面２８ｂと軸方向において対向している。   The axial end portion 41e of the annular protrusion 41 faces the side surface 28 of the flange 8 with a gap s1 therebetween. As shown in FIG. 2, the inner peripheral edge 41f of the axial end portion 41e is located slightly radially inward from the second corner portion 29b of the side surface 28 of the flange 8, and the inner peripheral edge 41f of the axial end portion 41e. Only faces the second side surface 28b in the axial direction.

また、環状突部４１は、密封装置１０を外輪２に装着した状態で、軸方向端部４１ｅの内周縁４１ｆと側面２８の第２角部２９ｂとの軸方向の隙間ｓ１が、例えば１．０ｍｍ程度（０．５〜１．５ｍｍ）となるように形成されている。この程度の隙間を生じさせることで、高速回転（例えば１０００ｒｐｍ）時において、軸方向端部４１ｅの内周縁４１ｆと、フランジ８の第２側部２８ｂにおける前記内周縁４１ｆと軸方向において対向する部分との間に表面張力により泥水ｗの膜が形成される。   Further, the annular protrusion 41 has an axial gap s1 between the inner peripheral edge 41f of the axial end portion 41e and the second corner portion 29b of the side surface 28 in a state where the sealing device 10 is mounted on the outer ring 2, for example, 1. It is formed to be about 0 mm (0.5 to 1.5 mm). By creating such a gap, a portion that faces the inner peripheral edge 41f of the axial end portion 41e and the inner peripheral edge 41f of the second side portion 28b of the flange 8 in the axial direction during high-speed rotation (for example, 1000 rpm). A film of muddy water w is formed by surface tension.

環状突部４１は、軸方向端部４１ｅの径方向中央部分に環状突部４１の周方向に沿った１本の環状溝４１ｈを有している。環状溝４１ｈは、断面Ｕ字状ないは断面半円形状に形成されている。また、環状溝４１ｈは、溝幅に比べて溝深さが浅い構成であり、溝幅は例えば０．４ｍｍ、溝深さは例えば０．２±０．１ｍｍとすることができる。環状溝４１ｈの深さ方向は軸方向となっている。   The annular protrusion 41 has one annular groove 41h along the circumferential direction of the annular protrusion 41 at the radial center portion of the axial end 41e. The annular groove 41h is formed in a U-shaped section or a semicircular section. Further, the annular groove 41h has a structure in which the groove depth is shallower than the groove width, and the groove width can be set to 0.4 mm, for example, and the groove depth can be set to 0.2 ± 0.1 mm, for example. The depth direction of the annular groove 41h is an axial direction.

外リップ部４５は、円筒状に形成されており、外輪２の端部外周面２２ａに当接している。外リップ部４５の軸方向端部４５ｅの内周側には、径内方向へ突出した環状の第２密封部４８が形成されている。この第２密封部４８は、外輪２に対して密封装置１０を装着する際に、外リップ部４５の軸方向端部４５ｅが径外方向へ拡径するように変形することで生じる外リップ部４５の弾性力により、外輪２の端部外周面２２ａに当接している。また、この第２密封部４８よりも外リップ部４５の基端側の部分は、端部外周面２２ａとの間に隙間が形成されている。これにより、第２密封部４８を端部外周面２２ａに全周にわたって線接触させて密封性能を高めている。   The outer lip portion 45 is formed in a cylindrical shape and is in contact with the outer peripheral surface 22 a of the end portion of the outer ring 2. On the inner peripheral side of the axial end portion 45e of the outer lip portion 45, an annular second sealing portion 48 protruding in the radially inward direction is formed. The second sealing portion 48 is an outer lip portion that is generated when the sealing device 10 is attached to the outer ring 2 and is deformed so that the axial end portion 45e of the outer lip portion 45 expands radially outward. The elastic force of 45 abuts against the outer peripheral surface 22 a of the end portion of the outer ring 2. In addition, a gap is formed between the portion on the proximal end side of the outer lip portion 45 with respect to the second sealing portion 48 and the end outer peripheral surface 22a. Thereby, the 2nd sealing part 48 is made to line-contact over the perimeter to the edge part outer peripheral surface 22a, and the sealing performance is improved.

上述の本発明の実施形態に係る密封装置１０によれば、環状突部４１の軸方向端部４１ｅの内周縁４１ｆと、フランジ８の第２側面２８ｂにおける前記内周縁４１ｆと軸方向に対向する部分との間に表面張力による泥水ｗの膜が生じ得る。また、密封装置１０は、環状突部４１の軸方向端部４１ｅに環状溝４１ｈを有しており、この環状溝４１ｈに泥水ｗを表面張力によって付着させて保持させることができる。このため、密封装置１０は、環状溝４１ｈを有さない従来のものよりも環状突部４１の軸方向端部４１ｅとフランジ８の第２側面２８ｂの間の泥水保持機能を向上させることができる（図２及び図３参照）。したがって、密封装置１０は、外部から内リップ部３１，３２，３３側への泥水ｗの浸入を抑えて耐泥水性能を向上させることができる。   According to the sealing device 10 according to the above-described embodiment of the present invention, the inner peripheral edge 41f of the axial end portion 41e of the annular protrusion 41 and the inner peripheral edge 41f of the second side surface 28b of the flange 8 are opposed in the axial direction. A film of muddy water w due to surface tension may be formed between the portions. Further, the sealing device 10 has an annular groove 41h at the axial end portion 41e of the annular protrusion 41, and mud water w can be attached to the annular groove 41h by surface tension and held. For this reason, the sealing device 10 can improve the muddy water holding function between the axial end 41e of the annular protrusion 41 and the second side surface 28b of the flange 8 as compared with the conventional device that does not have the annular groove 41h. (See FIGS. 2 and 3). Therefore, the sealing device 10 can suppress the intrusion of the muddy water w from the outside to the inner lip portions 31, 32, 33 side, and can improve the muddy water resistance.

［変形例］
なお、本発明は上述の実施形態に限定されるものではなく、特許請求の範囲内において種々の変更が可能である。例えば、環状溝４１ｈの断面は、Ｖ字状や断面矩形状であってもよい。また、環状溝４１ｈは、環状突部４１の軸方向端部４１ｅに複数本形成されていてもよい。さらに、環状溝４１ｈを含む軸方向端部４１ｅの全面がＲａ＝５〜８程度の粗面に形成されていてもよい。この粗面は、シール部材１２を成型する加硫金型の内面の軸方向端部４１ｅに対応する部分を放電加工によってＲａ＝５〜８程度の粗面にすることで、加硫成形時に形成することができる。この場合、軸方向端部４１ｅは環状溝４１ｈを備え且つ粗面加工されているので、環状溝４１ｈを備えているが粗面加工されていない場合よりも更に泥水保持機能を向上させることができる。 [Modification]
The present invention is not limited to the above-described embodiment, and various modifications can be made within the scope of the claims. For example, the annular groove 41h may have a V-shaped cross section or a rectangular cross section. A plurality of annular grooves 41 h may be formed in the axial end portion 41 e of the annular protrusion 41. Furthermore, the entire surface of the axial end portion 41e including the annular groove 41h may be formed as a rough surface with Ra = 5-8. This rough surface is formed at the time of vulcanization molding by making the portion corresponding to the axial end portion 41e of the inner surface of the vulcanization mold for molding the seal member 12 into a rough surface of Ra = 5 to 8 by electric discharge machining. can do. In this case, since the axial end 41e is provided with the annular groove 41h and is roughened, the muddy water retaining function can be further improved as compared with the case where the annular groove 41h is provided but is not roughened. .

１：車輪用転がり軸受装置、２：外輪、３：内軸、６ａ：シール面、８：フランジ、９：環状空間、１０：密封装置、１１：芯金、１２：シール部材、１６：円筒部、１７：外円環部、２０：外輪の軸方向端面、２１：外輪の端部内周面、２８：側面、２８ａ：シール面、３１，３２，３３：内リップ部、４１：環状突部、４１ｅ：環状突部の軸方向端部、４１ｈ：環状溝、ｓ１：隙間   DESCRIPTION OF SYMBOLS 1: Rolling bearing apparatus for wheels, 2: Outer ring, 3: Inner shaft, 6a: Seal surface, 8: Flange, 9: Annular space, 10: Sealing device, 11: Metal core, 12: Seal member, 16: Cylindrical part , 17: outer ring portion, 20: axial end surface of the outer ring, 21: inner peripheral surface of the end portion of the outer ring, 28: side surface, 28a: seal surface, 31, 32, 33: inner lip portion, 41: annular protrusion, 41e: axial end of the annular protrusion, 41h: annular groove, s1: gap

Claims (1)

同心状に配置された内軸と外輪とを備え、当該外輪の軸方向端面に間隔を隔てて対向する側面を有したフランジが前記内軸の端部に設けられた車輪用転がり軸受装置に用いられ、前記内軸と前記外輪との間の環状空間に泥水が浸入するのを防ぐ密封装置であって、
前記外輪の端部内周面に嵌合して当該外輪に固定される円筒部、及び当該円筒部から径方向外方へ延びて前記外輪の軸方向端面に当接する外円環部を有する芯金と、
前記内軸に設けられているシール面に摺接する内リップ部、及び前記内リップ部の径方向外方で前記フランジの側面に近づく側に延びて当該側面に対向する環状突部を有するシール部材と、を備え、
前記環状突部の軸方向端部は、表面張力により泥水の膜が生じ得る隙間を隔てて前記フランジの側面と対向しており、且つ環状溝を有しており、
前記環状溝が、前記環状突部と前記フランジの側面とが対向している径方向の領域よりも径方向外側に位置していることを特徴とする密封装置。 Used in a rolling bearing device for a wheel provided with a flange having an inner shaft and an outer ring arranged concentrically and having a side face facing the axial end face of the outer ring with a space therebetween. A sealing device for preventing muddy water from entering the annular space between the inner shaft and the outer ring,
A metal core having a cylindrical portion that is fitted to the inner peripheral surface of the end portion of the outer ring and is fixed to the outer ring, and an outer annular portion that extends radially outward from the cylindrical portion and contacts the axial end surface of the outer ring. When,
A seal member having an inner lip portion slidably in contact with a seal surface provided on the inner shaft, and an annular protrusion that extends radially outward of the inner lip portion toward the side of the flange and faces the side surface And comprising
The axial end of the annular protrusion is opposed to the side surface of the flange with a gap in which a muddy water film may be generated by surface tension, and has an annular groove .
The sealing device, wherein the annular groove is located on a radially outer side than a radial region where the annular protrusion and a side surface of the flange face each other.
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