JP2005331002A - Sealing device - Google Patents

Sealing device Download PDF

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Publication number
JP2005331002A
JP2005331002A JP2004148596A JP2004148596A JP2005331002A JP 2005331002 A JP2005331002 A JP 2005331002A JP 2004148596 A JP2004148596 A JP 2004148596A JP 2004148596 A JP2004148596 A JP 2004148596A JP 2005331002 A JP2005331002 A JP 2005331002A
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Japan
Prior art keywords
ring
outer peripheral
inner peripheral
seal
peripheral surface
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Pending
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JP2004148596A
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Japanese (ja)
Inventor
Naoto Kobayashi
直人 小林
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Nok Corp
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Nok Corp
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Priority to JP2004148596A priority Critical patent/JP2005331002A/en
Publication of JP2005331002A publication Critical patent/JP2005331002A/en
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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
    • F16C33/7869—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
    • F16C33/7879—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 further sealing ring
    • F16C33/7883—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 further sealing ring mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
    • 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
    • F16C33/783—Details of the sealing or parts thereof, e.g. geometry, material of the mounting 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Of Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To secure fitting force and sealability of a peripheral part of a fitting ring 1 in a sealing device without increasing dimension of the sealing device. <P>SOLUTION: The sealing device is provided with the fitting ring 1 having a peripheral cylinder part 11 to be fitted to the inner peripheral surface 111a of an outer ring 111 of a bearing 110 and seal lips 22 and 23 integrally provided with the fitting ring 1 and made of a rubber-like elastic material. A part of the peripheral cylinder part 11 in the axial direction is formed with a thin part 13, of which thickness is reduced toward the inner peripheral side, and the peripheral surface of the thin part 13 is formed with a seal projection 24 made of the rubber-like elastic material and to be tightly brought in contact with the inner peripheral surface 111a of the outer ring 111 with an appropriate margin h for crush. Outside diameter of a skirt part 26 of the seal projection 24 is formed smaller than the outside diameter of the peripheral cylinder part 11 of the fitting ring 1 to secure a clearance δ for allowing deformation for release due to crush of the seal projection 24. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、シールリップにより機器の回転部分を密封する密封装置に関するものである。   The present invention relates to a sealing device for sealing a rotating part of an apparatus with a sealing lip.

自動車の懸架装置に車輪を回転自在に支持する軸受は、密封装置によって泥水や塵埃から保護されており、このような密封装置としては、従来から、例えば下記の特許文献１に記載されたものが知られている。そして図５は、特許文献１に記載された従来技術による密封装置を、その軸心Ｏを通る平面で切断して示す装着状態の半断面図、図６は、特許文献１に記載された他の密封装置の一部を、軸心を通る平面で切断して示す部分断面図である。
特開２００４−１９８６５ A bearing for rotatably supporting a wheel on a suspension device of an automobile is protected from muddy water and dust by a sealing device. As such a sealing device, for example, one described in Patent Document 1 below has been conventionally used. Are known. FIG. 5 is a half sectional view showing a mounting state in which the sealing device according to the prior art described in Patent Document 1 is cut along a plane passing through the axis O, and FIG. It is a fragmentary sectional view which cut | disconnects and shows a part of sealing device of this by the plane which passes along an axial center.
JP2004-18865

まず図５において、参照符号１１０は、外輪１１１及び内輪１１２とその間に配置された鋼球１１３からなる軸受である。密封装置１００は、外輪１１１の内周面に圧入嵌着される金属製の取付環１０１にゴム状弾性材料で一体成形されたサイドリップ１０２及びラジアルリップ１０３と、内輪１１２の外周面に装着されるスリンガ１０４との組み合わせ構造であって、サイドリップ１０２がスリンガ１０４のシールフランジ１０４ａの内側面と摺動可能に密接され、ラジアルリップ１０３がスリンガ１０４のスリーブ１０４ｂの外周面と摺動可能に密接されることによって、軸受外部ＳＯから軸受内部ＳＩへの泥水や塵埃等の侵入を防止している。 First, in FIG. 5, reference numeral 110 is a bearing composed of an outer ring 111 and an inner ring 112 and a steel ball 113 disposed therebetween. The sealing device 100 is attached to the outer peripheral surface of the inner ring 112 and the side lip 102 and the radial lip 103 that are integrally formed of a rubber-like elastic material on a metal mounting ring 101 that is press-fitted to the inner peripheral surface of the outer ring 111. The side lip 102 is slidably in close contact with the inner surface of the seal flange 104a of the slinger 104, and the radial lip 103 is slidably in close contact with the outer peripheral surface of the sleeve 104b of the slinger 104. respectively, so that to prevent the intrusion of muddy water and dust from the outside of the bearing S O into the bearing interior S I.

また、この種の密封装置１００には、図５に二点鎖線で示されるように、スリンガ１０４のシールフランジ１０４ａの外側面に、磁性粉体を混入したゴム状弾性材料で円盤状に成形され円周方向交互に異なる磁極が着磁されたパルサーリング１０５が一体的に接着されたものがある。この場合、パルサーリング１０５の外側には、その外側面に近接対向させて磁気センサ１０６が配置される。したがって、不図示の車輪の回転によって、内輪１１２と共にスリンガ１０４と一体のパルサーリング１０５が回転すると、磁気センサ１０６から、その検出面の正面を交互に通過する磁極に応じてパルス信号が出力され、これによって車輪の回転速度等を検出することができるようになっている。   Further, in this type of sealing device 100, as shown by a two-dot chain line in FIG. 5, the outer surface of the seal flange 104a of the slinger 104 is molded into a disk shape with a rubber-like elastic material mixed with magnetic powder. There is a pulsar ring 105 in which different magnetic poles alternately magnetized in the circumferential direction are integrally bonded. In this case, the magnetic sensor 106 is disposed on the outer side of the pulsar ring 105 so as to face and face the outer surface. Accordingly, when the pulsar ring 105 integral with the slinger 104 is rotated together with the inner ring 112 by rotation of a wheel (not shown), a pulse signal is output from the magnetic sensor 106 according to the magnetic poles alternately passing through the front of the detection surface. As a result, the rotational speed of the wheel can be detected.

ここで、図５に示される構造では、サイドリップ１０２及びラジアルリップ１０３を一体に保持している取付環１０１の外周筒部１０１ａが、外輪１１１の内周面に金属嵌合しているのみであるため、この部分の密封性は充分ではない。そこで、外輪１１１に対する取付環１０１の嵌合力を確保すると共に、外輪１１１と取付環１０１との間の密封性を向上させるためには、図６に示されるように、取付環１０１における外周筒部１０１ａの先端側に、内周側へテーパ状に屈曲した絞り部１０１ｂを形成し、サイドリップ１０２から取付環１０１の内側面を覆うように延びるゴム層１０７の外周部を、前記絞り部１０１ｂの外周面に廻してシール突条１０８を一体的に成形し、外輪１１１の内周面に、取付環１０１の外周筒部１０１ａを金属嵌合させると共に、シール突条１０８を適当なつぶし代をもって密接させることが知られている。   Here, in the structure shown in FIG. 5, the outer peripheral cylindrical portion 101 a of the mounting ring 101 that integrally holds the side lip 102 and the radial lip 103 is only metal-fitted to the inner peripheral surface of the outer ring 111. For this reason, the sealability of this part is not sufficient. Therefore, in order to ensure the fitting force of the mounting ring 101 to the outer ring 111 and to improve the sealing performance between the outer ring 111 and the mounting ring 101, as shown in FIG. A throttle part 101b that is bent in a taper shape toward the inner peripheral side is formed on the distal end side of 101a, and the outer peripheral part of the rubber layer 107 that extends from the side lip 102 so as to cover the inner side surface of the mounting ring 101 is formed on the tip part of the throttle part 101b. The seal protrusion 108 is integrally formed around the outer peripheral surface, and the outer peripheral cylindrical portion 101a of the mounting ring 101 is metal-fitted to the inner peripheral surface of the outer ring 111, and the seal protrusion 108 is closely contacted with an appropriate crushing margin. It is known to let

ところが、図６のような構成においては、シール突条１０８を内周側からバックアップする絞り部１０１ｂが、内周側への屈曲形状であるため、その内周を包囲するように成形されたゴム層１０７の内周面と、外輪１１１の内周面との間の径方向厚さｔ’が、図５に示される密封装置１００における同部分の径方向厚さｔよりも著しく大きくなってしまう。そしてこの種の密封装置１００の場合、スリンガ１０４の存在により、径方向厚さｔ’を内周側へ拡大することはできないので、密封装置１００の径方向取付スペースを大きくする必要があった。   However, in the configuration as shown in FIG. 6, the narrowed portion 101b that backs up the seal protrusion 108 from the inner peripheral side has a bent shape toward the inner peripheral side, so that the rubber is formed so as to surround the inner periphery. The radial thickness t ′ between the inner peripheral surface of the layer 107 and the inner peripheral surface of the outer ring 111 is significantly larger than the radial thickness t of the same portion in the sealing device 100 shown in FIG. . In the case of this type of sealing device 100, since the radial thickness t 'cannot be increased to the inner peripheral side due to the presence of the slinger 104, it is necessary to increase the radial mounting space of the sealing device 100.

また、絞り部１０１ｂの外周側に形成されたシール突条１０８のボリュームが比較的大きいものとなるので、密封装置１００を外輪１１１の内周に圧入する際に、シール突条１０８が外輪１１１の内周の開口縁によってしごかれて損傷するおそれがあった。   Further, since the volume of the seal protrusion 108 formed on the outer peripheral side of the throttle portion 101b is relatively large, when the sealing device 100 is press-fitted into the inner periphery of the outer ring 111, the seal protrusion 108 is formed on the outer ring 111. There was a risk of damaging and damage by the opening edge of the inner periphery.

本発明は、以上のような点に鑑みてなされたものであって、その技術的課題は、密封装置における取付環外周部の嵌合力及び密封性を、密封装置の寸法拡大を来さずに確保することにある。   The present invention has been made in view of the above points, and its technical problem is that the fitting force and the sealing performance of the outer periphery of the mounting ring in the sealing device can be reduced without enlarging the size of the sealing device. It is to secure.

上述した技術的課題を有効に解決するための手段として、請求項１の発明に係る密封装置は、外周部材の内周面に嵌着される外周筒部を有する取付環と、この取付環に一体的に設けられゴム状弾性材料からなるシールリップとを備え、前記外周筒部の軸方向一部に、その肉厚を内周側へ減少させた薄肉部が形成され、この薄肉部の外周面に、ゴム状弾性材料からなり前記外周部材の内周面に適当なつぶし代をもって密接されるシール突条を形成してなるものである。   As means for effectively solving the technical problem described above, a sealing device according to the invention of claim 1 includes an attachment ring having an outer peripheral cylindrical portion fitted to an inner peripheral surface of an outer peripheral member, and an attachment ring. And a seal lip made of a rubber-like elastic material, and a thin portion with a reduced thickness toward the inner peripheral side is formed on a part of the outer peripheral cylindrical portion in the axial direction. The surface is formed with a seal ridge made of a rubber-like elastic material and in close contact with the inner peripheral surface of the outer peripheral member with an appropriate crushing allowance.

すなわち請求項１に記載された構成においては、取付環における外周筒部の一部を薄肉とすることによって、シール突条の形成スペースを確保しているものである。   That is, in the structure described in Claim 1, the space for forming the seal protrusion is secured by thinning a part of the outer peripheral cylindrical portion of the mounting ring.

請求項２の発明に係る密封装置は、シール突条の裾部の外径が、取付環の外周筒部の外径よりも小径に形成されたものである。   In the sealing device according to the second aspect of the present invention, the outer diameter of the skirt portion of the seal protrusion is formed smaller than the outer diameter of the outer peripheral cylindrical portion of the mounting ring.

すなわち請求項２に記載された構成においては、シール突条の裾部が、取付環の外周筒部の外径よりも小径であることによって、外周部材の内周面との間に、シール突条の逃げ変形を許容する隙間が形成されるので、シール突条が径方向のつぶしを受けることによる応力が、前記逃げ変形により吸収される。   That is, in the configuration described in claim 2, the skirt portion of the seal protrusion is smaller in diameter than the outer diameter of the outer peripheral cylindrical portion of the mounting ring, so that the seal protrusion is formed between the inner peripheral surface of the outer peripheral member. Since the gap that allows the strip to deform is formed, the stress caused by the radial deformation of the seal protrusion is absorbed by the clearance.

請求項１の発明に係る密封装置によれば、取付環の外周筒部が、外周部材の内周面に嵌着されることによって固定されると共に、シール突条によって外周部材の内周面との間の密封性が確保される。そして、取付環における外周筒部の一部を薄肉とすることによって、シール突条の形成スペースを確保しているので、シール突条による径寸法の増大を来さない。   According to the sealing device of the first aspect of the invention, the outer peripheral cylindrical portion of the mounting ring is fixed by being fitted to the inner peripheral surface of the outer peripheral member, and the inner peripheral surface of the outer peripheral member is sealed by the seal protrusion. The sealing performance between the two is ensured. And since the formation space of a seal protrusion is ensured by making a part of outer peripheral cylinder part in an attachment ring thin, the increase in the diameter dimension by a seal protrusion does not come.

請求項２の発明に係る密封装置によれば、外周部材の内周面にシール突条が圧縮状態に密接されることによる応力が有効に吸収されるので、シール突条のはみ出しや、応力緩和（ヘタリ）による密封性の低下を防止することができる。   According to the sealing device of the second aspect of the present invention, since the stress caused by the seal protrusion being brought into close contact with the inner peripheral surface of the outer peripheral member is effectively absorbed, the protrusion of the seal protrusion or stress relaxation is achieved. It is possible to prevent the sealing performance from being deteriorated due to (slip).

以下、本発明に係る密封装置を、自動車用車輪懸架装置に車輪を回転自在に支持する軸受部を密封する密封手段について実施した好ましい形態を、図面を参照しながら説明する。図１は、本発明の第一の形態を、その軸心Ｏを通る平面で切断して示す装着状態の半断面図、図２は、要部断面図である。   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments in which a sealing device according to the present invention is implemented with respect to a sealing means for sealing a bearing portion that rotatably supports a wheel on an automobile wheel suspension will be described with reference to the drawings. FIG. 1 is a half cross-sectional view showing a first embodiment of the present invention cut along a plane passing through the axis O, and FIG. 2 is a cross-sectional view of a main part.

図１における参照符号１１０は、自動車の懸架装置において、車輪を回転自在に支持するための軸受であって、外輪１１１及び内輪１１２と、その間に配置され円周方向に並んだ多数の鋼球１１３（図１には１個のみ示される）からなる。外輪１１１は非回転であって、懸架装置における不図示のナックルに固定され、内輪１１２は車輪側の不図示のハブに一体的に嵌着されている。   Reference numeral 110 in FIG. 1 is a bearing for rotatably supporting a wheel in a suspension system of an automobile, and includes an outer ring 111 and an inner ring 112, and a number of steel balls 113 arranged therebetween and arranged in the circumferential direction. (Only one is shown in FIG. 1). The outer ring 111 is non-rotating and is fixed to a knuckle (not shown) in the suspension device, and the inner ring 112 is integrally fitted to a hub (not shown) on the wheel side.

本発明に係る密封装置は、軸受１１０の内部ＳＩへ、外部ＳＯからの泥水や塵埃等が侵入するのを防止すると共に、鋼球１１３を潤滑するグリースが軸受外部ＳＯへ流出するのを防止するもので、外輪１１１の内周面に圧入嵌着される取付環１と、この取付環１に一体的に設けられたシールリング２と、内輪１１２の外周面に装着されるスリンガ３とを備える。 Sealing device according to the present invention, the interior S I of the bearing 110, thereby preventing the muddy water and dust from the outside S O from entering, the grease for lubricating the steel balls 113 from flowing out to the outside of the bearing S O A mounting ring 1 that is press-fitted to the inner peripheral surface of the outer ring 111, a seal ring 2 that is provided integrally with the mounting ring 1, and a slinger 3 that is mounted on the outer peripheral surface of the inner ring 112. With.

取付環１は、鋼板等の金属板を打ち抜きプレス成形することにより製作したものであって、軸心Ｏを通る平面で切断した形状（図１の断面形状）が略Ｌ字形をなし、すなわち軸受１１０の外輪１１１の内周面１１１ａに圧入嵌着される外周筒部１１と、その軸受１１０の内部ＳＩ側の端部から内周側へ延びる内周鍔部１２からなる。 The mounting ring 1 is manufactured by punching and pressing a metal plate such as a steel plate, and the shape cut in a plane passing through the axis O (cross-sectional shape in FIG. 1) is substantially L-shaped, that is, a bearing. an outer peripheral tube portion 11 which is pressure inserted and fitted to the inner circumferential surface 111a of the outer ring 111 of 110, consisting of inner peripheral flange portion 12 extending to the inner peripheral side from an end portion of the internal S I side of the bearing 110.

シールリング２は、所定のゴム加硫成形用金型（不図示）内に、予め加硫接着剤を塗布した取付環１を位置決めセットして型締めし、前記金型と取付環１との間に画成された成形用キャビティ内に、未加硫ゴム材料を充填し、加熱・加圧することによって、加硫成形と取付環１への加硫接着を同時に行ったものである。このシールリング２は、取付環１における外周筒部１１の内周面から内周鍔部１２の内側面にかけて一体的に加硫接着された基部ゴム層２１と、その内周部から延びるサイドリップ２２及びラジアルリップ２３からなる。サイドリップ２２及びラジアルリップ２３は、請求項１に記載されたシールリップに相当する。   The seal ring 2 is set in a predetermined rubber vulcanization mold (not shown) by positioning and clamping the mounting ring 1 previously coated with a vulcanizing adhesive. An unvulcanized rubber material is filled in a molding cavity defined in between, and heated and pressurized to perform vulcanization molding and vulcanization adhesion to the mounting ring 1 at the same time. The seal ring 2 includes a base rubber layer 21 integrally vulcanized and bonded from the inner peripheral surface of the outer peripheral cylindrical portion 11 to the inner side surface of the inner peripheral flange portion 12 in the mounting ring 1, and a side lip extending from the inner peripheral portion. 22 and radial lip 23. The side lip 22 and the radial lip 23 correspond to the seal lip described in claim 1.

スリンガ３は、鋼板等の金属板を打ち抜きプレス成形することにより製作したものであって、軸心Ｏを通る平面で切断した形状（図１の断面形状）が略Ｌ字形をなす。すなわち軸受１１０の内輪１１２の外周面１１２ａに圧入嵌着される内周筒部３１と、その軸受外部ＳＯ側の端部から外周側へ軸心と直交する平面状に展開した円盤状のシールフランジ３２とからなる。シールフランジ３２の外径は、取付環１における外周筒部１１の内周面に形成された基部ゴム層２１の外端部２１ａの内周面よりも小径であり、したがって両者２１ａ，３２の間には、環状の隙間Ｇが存在する。 The slinger 3 is manufactured by punching and pressing a metal plate such as a steel plate, and the shape (cross-sectional shape in FIG. 1) cut along a plane passing through the axis O forms a substantially L shape. Seal or an inner peripheral tube portion 31 which is pressure inserted and fitted to the outer peripheral surface 112a of the inner ring 112 of the bearing 110, the bearing outer S O side from the end disc-shaped developed in the plane perpendicular to the axis to the outer peripheral side It consists of a flange 32. The outer diameter of the seal flange 32 is smaller than the inner peripheral surface of the outer end portion 21 a of the base rubber layer 21 formed on the inner peripheral surface of the outer peripheral cylindrical portion 11 in the mounting ring 1. There is an annular gap G.

シールリング２におけるサイドリップ２２は、先端部側が大径となるように開いた円錐状に展開した形状に成形されたものであって、スリンガ３のシールフランジ３２との間で適当に軸方向変形を受けた状態で、先端近傍が、軸心Ｏに対して略垂直な平面状をなすシールフランジ３２の内側面３２ａに、摺動可能に密接される。   The side lip 22 in the seal ring 2 is formed in a conical shape that is open so that the tip side has a large diameter, and is appropriately deformed in the axial direction between the seal flange 32 of the slinger 3. In the state of receiving, the vicinity of the tip is slidably brought into close contact with the inner side surface 32a of the seal flange 32 having a planar shape substantially perpendicular to the axis O.

シールリング２におけるラジアルリップ２３は、基部ゴム層２１の内周端であってサイドリップ２２の根元２２ａよりも内周側の位置から、軸受内部ＳＩと反対側へ向けて突出している。このラジアルリップ２３における先端部の内周に略Ｖ字形の突出形状に形成されたシールエッジの内径は、スリンガ３の内周筒部３１の外径よりも小径に成形されており、したがって図１に示される装着状態では、スリンガ３の内周筒部３１の外周面３１ａに、適当な締め代をもって摺動可能に密接される。 Radial lip 23 of the seal ring 2 is from the position of the inner circumferential side of the base 22a of the side lip 22 a inner peripheral edge of the base rubber layer 21, and protrudes toward the opposite side to the bearing inner S I. The inner diameter of the seal edge formed in a substantially V-shaped projecting shape on the inner periphery of the distal end portion of the radial lip 23 is formed to be smaller than the outer diameter of the inner peripheral cylindrical portion 31 of the slinger 3. In the mounted state shown in Fig. 2, the outer peripheral surface 31a of the inner peripheral cylindrical portion 31 of the slinger 3 is slidably in contact with an appropriate margin.

取付環１における外周筒部１１は、軸受１１０の外輪１１１の内周面１１１ａに適当な締め代をもって圧入されるように、外径が、前記外輪１１１の内周面１１１ａより僅かに大径に形成されており、その先端寄りの部分には、肉厚を内周側へ減少させた薄肉部１３が形成されている。言い換えれば、この薄肉部１３は、外周筒部１１における先端寄りの外周面に、円周方向へ連続した凹部を加工することによって形成されたもので、すなわち図２に示されるように、薄肉部１３の肉厚ｔ１３は、外周筒部１１の肉厚ｔ１１よりも内周側へｄだけ小さいものとなっている。なお薄肉部１３の肉厚ｔ１３は、外周筒部１１の肉厚ｔ１１にもよるが、好ましくは、肉厚ｔ１１の50〜80％とする。 The outer peripheral cylindrical portion 11 in the mounting ring 1 has a slightly larger outer diameter than the inner peripheral surface 111a of the outer ring 111 so that the outer peripheral cylindrical portion 11 is press-fitted into the inner peripheral surface 111a of the outer ring 111 of the bearing 110 with an appropriate margin. A thin portion 13 having a reduced thickness toward the inner periphery is formed at a portion near the tip. In other words, the thin wall portion 13 is formed by processing a concave portion continuous in the circumferential direction on the outer peripheral surface near the tip of the outer peripheral cylindrical portion 11, that is, as shown in FIG. The wall thickness t 13 of 13 is smaller than the wall thickness t 11 of the outer peripheral cylindrical portion 11 by d toward the inner peripheral side. Note the thickness t 13 of the thin portion 13, depending on the thickness t 11 of the outer tubular portion 11, preferably, 50 to 80% of the wall thickness t 11.

取付環１における薄肉部１３の外周面には、ゴム状弾性材料からなり円周方向へ連続したシール突条２４が形成されている。詳しくは、シールリング２における基部ゴム層２１の外端部２１ａからは、取付環１の薄肉部１３の先端面を覆う端面ゴム層２５及び前記薄肉部１３の外周面を覆う外周ゴム層２６が、連続して形成されており、シール突条２４は、前記外周ゴム層２６に、略Ｖ字の山形の断面形状をなすように形成されている。   On the outer peripheral surface of the thin wall portion 13 in the mounting ring 1, a seal protrusion 24 made of a rubber-like elastic material and continuous in the circumferential direction is formed. Specifically, from the outer end 21 a of the base rubber layer 21 in the seal ring 2, there are an end rubber layer 25 covering the distal end surface of the thin portion 13 of the mounting ring 1 and an outer peripheral rubber layer 26 covering the outer peripheral surface of the thin portion 13. The seal protrusion 24 is formed on the outer peripheral rubber layer 26 so as to have a substantially V-shaped cross-sectional shape.

取付環１の外周筒部１１の外周面に対するシール突条２４の突出高さｈは、図１に示される装着状態において、軸受１１０の外輪１１１の内周面１１１ａに密接した時のつぶし代に相当するものである。そしてこの突出高さｈは、つぶしによる密封面圧と、外輪１１１の内周面１１１ａへの圧入過程での抵抗によるむしれなどを考慮して、適切に決定される。   The protruding height h of the seal protrusion 24 with respect to the outer peripheral surface of the outer peripheral cylindrical portion 11 of the mounting ring 1 is a crushing allowance when it is in close contact with the inner peripheral surface 111a of the outer ring 111 of the bearing 110 in the mounted state shown in FIG. It is equivalent. The protrusion height h is appropriately determined in consideration of the sealing surface pressure due to crushing and the sag due to resistance in the press-fitting process into the inner peripheral surface 111a of the outer ring 111.

シール突条２４が形成された外周ゴム層２６は、請求項２に記載された裾部に相当する部分であって、その外径は、取付環１の外周筒部１１の外径よりも小さく、言い換えれば、前記外周ゴム層２６の径方向肉厚ｔ２６は、取付環１における外周筒部１１と薄肉部１３の肉厚ｔ１１，ｔ１３の差ｄよりも適宜小さく形成されている。そして、前記外周筒部１１の外径と外周ゴム層２６の外径との差、すなわちｄ−ｔ２６は、シール突条２４が外輪１１１の内周面１１１ａにｈだけつぶされた状態で密接された時の逃げ変形を許容する隙間δとなるものである。 The outer peripheral rubber layer 26 on which the seal protrusions 24 are formed is a portion corresponding to the skirt described in claim 2, and the outer diameter thereof is smaller than the outer diameter of the outer peripheral cylindrical portion 11 of the mounting ring 1. , in other words, the radial thickness t 26 of the outer peripheral rubber layer 26 is suitably smaller than the difference d of the thickness t 11, t 13 of the outer tube portion 11 and the thin portion 13 of the mounting ring 1. The difference between the outer diameter of the outer peripheral cylindrical portion 11 and the outer diameter of the outer peripheral rubber layer 26, that is, dt 26, is in close contact with the seal protrusion 24 crushed on the inner peripheral surface 111 a of the outer ring 111 by h. This is the gap δ that allows the escaping deformation.

なお、外周ゴム層２６におけるシール突条２４の形成位置は、外輪１１１の面取り部１１１ｂの大きさのばらつきや、取付環１の圧入位置のばらつき等を考慮して、シール突条２４が外輪１１１の内周面１１１ａから外れることのない位置とすることは当然であり、シール突条２４の本数も１本には限定されない。また、外輪１１１への取付環１の圧入は、端面ゴム層２５を軸方向へ押すことにより行われる。したがって、この端面ゴム層２５の肉厚ｔ２５は、厚すぎると圧入不足や端面ゴム層２５の破損を来すので、好ましくは、例えば0.1〜0.5ｍｍ程度の適切な大きさに設定される。 The seal protrusion 24 is formed on the outer peripheral rubber layer 26 in consideration of variations in the size of the chamfered portion 111b of the outer ring 111, variations in the press-fitting position of the mounting ring 1, and the like. Naturally, the position does not deviate from the inner peripheral surface 111a, and the number of seal protrusions 24 is not limited to one. Further, the fitting ring 1 is press-fitted into the outer ring 111 by pushing the end face rubber layer 25 in the axial direction. Accordingly, the wall thickness t 25 of the end face rubber layer 25 is preferably set to an appropriate size of about 0.1 to 0.5 mm, for example, because press fitting or damage to the end face rubber layer 25 is caused if it is too thick.

以上の構成を備える密封装置は、図１に示されるように、取付環１の外周筒部１１において軸受１１０の外輪１１１の内周面１１１ａに圧入嵌着され、この取付環１に一体に設けられたゴム状弾性材料からなるシールリング２のサイドリップ２２及びラジアルリップ２３が、軸受１１０の内輪１１２と一体的に回転するスリンガ３のシールフランジ３２及び内周筒部３１に、摺動可能に密接されることによって、軸受１１０の外部ＳＯから内部ＳＩへ塵埃や泥水等が侵入するのを防止すると共に、軸受１１０の内部ＳＩで鋼球１１３を潤滑している不図示のグリースの流出を防止するものである。 As shown in FIG. 1, the sealing device having the above configuration is press-fitted to the inner peripheral surface 111 a of the outer ring 111 of the bearing 110 in the outer peripheral cylindrical portion 11 of the mounting ring 1, and is provided integrally with the mounting ring 1. The side lip 22 and the radial lip 23 of the seal ring 2 made of a rubber-like elastic material are slidable on the seal flange 32 and the inner peripheral cylindrical portion 31 of the slinger 3 that rotates integrally with the inner ring 112 of the bearing 110. by being close contact, from the outside S O of the bearing 110 along with dust and muddy water into the interior S I is prevented from entering, not shown, which lubricates the steel balls 113 within S I of the bearing 110 grease Prevents outflow.

スリンガ３のシールフランジ３２は、回転によって、これと接触する流体や異物に対して遠心力を与えるので、軸受外部ＳＯ側から、シールフランジ３２の外周の隙間Ｇを通じてサイドリップ２２とシールフランジ３２の摺動部へ介入しようとする泥水等は、前記遠心力によって振り切られ、外周側へ排除される。また、僅かな泥水等が、サイドリップ２２とシールフランジ３２との摺動部を内周側へ通過したとしても、この泥水等は、ラジアルリップ２３とスリンガ３の内周筒部３１との摺動部において封止されるので、シールフランジ３２の振り切り作用によって、このシールフランジ３２とサイドリップ２２との摺動部へ押し戻され、更にその外周から軸受外部ＳＯ側へ排出される。 Since the seal flange 32 of the slinger 3 applies a centrifugal force to the fluid and foreign matter that come into contact with the slinger 3 by rotation, the side lip 22 and the seal flange 32 are passed through the gap G on the outer periphery of the seal flange 32 from the bearing external SO side. The muddy water or the like trying to intervene in the sliding portion is shaken off by the centrifugal force and removed to the outer peripheral side. Even if a small amount of muddy water passes through the sliding portion between the side lip 22 and the seal flange 32 toward the inner peripheral side, the muddy water is slid between the radial lip 23 and the inner peripheral cylindrical portion 31 of the slinger 3. Since it is sealed at the moving part, it is pushed back to the sliding part between the seal flange 32 and the side lip 22 by the swinging action of the seal flange 32, and further discharged from the outer periphery to the bearing external SO side.

また、この形態によれば、取付環１の外周筒部１１が、外輪１１１の内周面１１１ａに圧入嵌着されることにより、取付環１及びこれと一体のシールリング２が所要の抜け抵抗をもって固定されると共に、シール突条２４によって外輪１１１の内周面１１１ａとの間の密封性が確保される。   Further, according to this embodiment, the outer peripheral cylindrical portion 11 of the mounting ring 1 is press-fitted and fitted to the inner peripheral surface 111a of the outer ring 111, so that the mounting ring 1 and the seal ring 2 integral with the mounting ring 1 have the required resistance to coming off. And the sealing protrusion 24 ensures the sealing performance with the inner peripheral surface 111a of the outer ring 111.

しかも、取付環１における外周筒部１１の一部を、肉厚を内周側へ減少させた薄肉部１３とすることによって、シール突条２４の形成スペースを確保しているので、取付環１の外周筒部１１の外周面から基部ゴム層２１の外端部２１ａの内周面間の肉厚ｔが、先に説明した図６の従来構造に比較して、著しく小さく抑えることができる。このため、密封装置の径寸法の増大を来さない。   In addition, since a part of the outer peripheral cylindrical portion 11 in the mounting ring 1 is a thin portion 13 having a reduced thickness toward the inner peripheral side, a space for forming the seal protrusion 24 is secured. The wall thickness t between the outer peripheral surface of the outer peripheral cylindrical portion 11 and the inner peripheral surface of the outer end portion 21a of the base rubber layer 21 can be significantly reduced as compared with the conventional structure shown in FIG. For this reason, the diameter of the sealing device does not increase.

ここで図３は、外周ゴム層２６と外輪１１１の内周面１１１ａとの間に、図２のような隙間δを設けなかった場合の比較例を示す要部断面図である。すなわちこの比較例の構成によれば、取付環１を外輪１１１に圧入する際に、つぶされるシール突条２４の逃げによって外周ゴム層２６が膨らむので、圧入過程で外輪１１１の面取り部１１１ｂにしごかれて、図３に示されるように外周ゴム層２６のはみ出し２６ａが発生したり、シール突条２４が面取り部１１１ｂに強くしごかれてちぎれるなど損傷の発生が懸念される。しかも、シール突条２４のつぶれによる応力が大きくなって、経時的な応力緩和（ヘタリ）が起こりやすくなることが懸念される。   Here, FIG. 3 is a cross-sectional view of an essential part showing a comparative example in the case where the gap δ as shown in FIG. 2 is not provided between the outer peripheral rubber layer 26 and the inner peripheral surface 111a of the outer ring 111. That is, according to the configuration of this comparative example, when the mounting ring 1 is press-fitted into the outer ring 111, the outer peripheral rubber layer 26 swells due to the escape of the crushed seal protrusion 24, so that the chamfered portion 111 b of the outer ring 111 is pressed in the press-fitting process. As shown in FIG. 3, there is a concern about the occurrence of damage such as the protrusion 26a of the outer peripheral rubber layer 26 or the seal protrusion 24 being strongly squeezed and broken by the chamfered portion 111b. In addition, there is a concern that stress due to the collapse of the seal protrusions 24 becomes large, and stress relaxation (sagging) with time tends to occur.

これに対し、図１及び図２に示される形態では、上述のように、隙間δの存在によってシール突条２４のつぶれによる容易な逃げ変形が許容され、かつシール突条２４が略Ｖ字の山形断面をなすことによって、径方向のつぶしに対する剛性が比較的低くなっているので、シール突条２４のヘタリによる密封性の低下や、外周ゴム層２６のはみ出し等が有効に防止される。また、シール突条２４は、図１の装着状態では完全につぶされた状態となるが、つぶれによる面圧の極大部がほぼ線状に分布することになるので、優れた密封性を奏する。しかも当該密封装置を外輪１１１の内周に圧入する際に、シール突条２４が柔軟に変形するので、外輪１１１の面取り部１１１ｂにしごかれて損傷するのを有効に防止することができる。   On the other hand, in the form shown in FIGS. 1 and 2, as described above, easy clearance deformation due to the collapse of the seal protrusion 24 is allowed due to the presence of the gap δ, and the seal protrusion 24 is substantially V-shaped. By forming the chevron-shaped cross section, the rigidity against squeezing in the radial direction is relatively low, so that deterioration of the sealing performance due to the settling of the seal protrusion 24 and the protrusion of the outer peripheral rubber layer 26 are effectively prevented. Further, the seal protrusion 24 is in a completely crushed state in the mounted state of FIG. 1, but the maximum portion of the surface pressure due to the crushed is distributed almost linearly, so that excellent sealing performance is achieved. In addition, when the sealing device is press-fitted into the inner periphery of the outer ring 111, the seal protrusion 24 is deformed flexibly, so that the chamfered portion 111b of the outer ring 111 can be effectively prevented from being damaged.

次に図４は、本発明の第二の形態を示す要部断面図である。この形態において、上述した第一の形態と異なるところは、シール突条２４が略台形の断面形状、すなわち軸受の外輪１１１の内周面１１１ａに対する密接面２４ａが軸方向に適当な幅をもった平面状をなし、その両側が斜面をなす形状に形成されたことにある。その他の部分は、図示が省略されているが、基本的に図１と略同様の構成を備える。   Next, FIG. 4 is a cross-sectional view of a main part showing a second embodiment of the present invention. In this embodiment, the difference from the first embodiment described above is that the seal protrusion 24 has a substantially trapezoidal cross-sectional shape, that is, the contact surface 24a with respect to the inner peripheral surface 111a of the outer ring 111 of the bearing has an appropriate width in the axial direction. It is in the shape of a flat surface with both sides forming a slope. Although the other parts are omitted in the drawing, they basically have the same configuration as that shown in FIG.

この形態においても、シール突条２４が形成された外周ゴム層２６の外径は、取付環１の外周筒部１１の外径よりも小さく、すなわち、前記外周ゴム層２６の径方向肉厚ｔ２６は、取付環１における外周筒部１１と薄肉部１３の肉厚ｔ１１，ｔ１３の差ｄよりも適宜小さく、このため、シール突条２４が外輪１１１の内周面１１１ａにｈだけつぶされた状態で密接された時の逃げ変形を許容する隙間δ
（＝ｄ−ｔ２６）を有する。 Also in this form, the outer diameter of the outer peripheral rubber layer 26 on which the seal protrusions 24 are formed is smaller than the outer diameter of the outer peripheral cylindrical portion 11 of the mounting ring 1, that is, the radial thickness t of the outer peripheral rubber layer 26 26 is appropriately smaller than the difference d between the thicknesses t 11 and t 13 of the outer peripheral cylindrical portion 11 and the thin wall portion 13 in the mounting ring 1, and therefore the seal protrusion 24 is crushed by h on the inner peripheral surface 111 a of the outer ring 111. Clearance δ allowing clearance deformation when in close contact with each other
(= D−t 26 ).

したがって、この構成によれば、シール突条２４の軸方向幅が図２のものに比較して大きいため、径方向のつぶしに対する剛性は大きくなるが、隙間δへの逃げ変形によって、圧縮応力がある程度吸収されるので、シール突条２４のヘタリによる密封性の低下や、外周ゴム層２６のはみ出し等が有効に防止される。また、外輪１１１の内周面１１１ａに対する密接面２４ａが軸方向に適当な幅を有する帯状に延びるため、優れた密封性を確保することができる。   Therefore, according to this configuration, since the axial width of the seal protrusion 24 is larger than that in FIG. 2, the rigidity against radial crushing is increased, but the compressive stress is reduced by the escape deformation to the gap δ. Since it is absorbed to some extent, it is possible to effectively prevent deterioration of the sealing performance due to the sticking of the sealing protrusion 24 and the protrusion of the outer peripheral rubber layer 26. Moreover, since the contact surface 24a with respect to the inner peripheral surface 111a of the outer ring 111 extends in a belt shape having an appropriate width in the axial direction, excellent sealing performance can be ensured.

なお、図１に二点鎖線で示されるように、スリンガ３のシールフランジ３２の外側面に、磁性粉体を混入したゴム状弾性材料で円盤状に成形され円周方向交互に異なる磁極が着磁されたパルサーリング４が一体的に接着されると共に、このパルサーリング４に磁気センサ５を対向配置することによって、車輪の回転速度等を検出可能とした密封装置についても、本発明を、上述の形態と同様に実施することができる。   In addition, as shown by a two-dot chain line in FIG. 1, magnetic poles that are formed in a disc shape with a rubber-like elastic material mixed with magnetic powder are applied to the outer surface of the seal flange 32 of the slinger 3 in the circumferential direction. The present invention also relates to a sealing device in which the magnetized pulsar ring 4 is integrally bonded, and the rotational speed of the wheel can be detected by disposing the magnetic sensor 5 opposite to the pulsar ring 4. It can implement similarly to the form of.

本発明に係る密封装置の好ましい実施の形態を、その軸心Ｏを通る平面で切断して示す装着状態の半断面図である。1 is a half sectional view of a mounting state in which a preferred embodiment of a sealing device according to the present invention is cut along a plane passing through its axis O. FIG. 図１の密封装置における要部断面図である。It is principal part sectional drawing in the sealing device of FIG. 比較例を示す要部断面図である。It is principal part sectional drawing which shows a comparative example. 本発明に係る密封装置の好ましい実施の形態を、その軸心Ｏを通る平面で切断して示す半断面図である。1 is a half sectional view showing a preferred embodiment of a sealing device according to the present invention by cutting along a plane passing through its axis O. FIG. 従来技術による密封装置を、その軸心Ｏを通る平面で切断して示す装着状態の半断面図である。1 is a half sectional view of a mounting state in which a sealing device according to the prior art is cut along a plane passing through its axis O. FIG. 従来技術による他の密封装置の一部を、軸心を通る平面で切断して示す部分断面図である。It is a fragmentary sectional view which cuts and shows a part of other sealing device by a prior art by the plane which passes along an axial center.

符号の説明Explanation of symbols

１１０ 軸受
１１１ 外輪（外周部材）
１１１ａ 内周面
１１２ 内輪
１１３ 鋼球
１ 取付環
１１ 外周筒部
１２ 内周鍔部
１３ 薄肉部
２ シールリング
２１ 基部ゴム層
２１ａ 外端部
２２ サイドリップ（シールリップ）
２３ ラジアルリップ（シールリップ）
２４ シール突条
２４ａ 密接面
２５ 端面ゴム層
２６ 外周ゴム層（裾部）
３ スリンガ
３１ 内周筒部
３２ シールフランジ
４ パルサーリング
５ 磁気センサ
Ｇ，δ 隙間 110 Bearing 111 Outer ring (outer peripheral member)
111a inner peripheral surface 112 inner ring 113 steel ball 1 mounting ring 11 outer peripheral cylindrical portion 12 inner peripheral flange portion 13 thin wall portion 2 seal ring 21 base rubber layer 21a outer end portion 22 side lip (seal lip)
23 Radial Lip (Seal Lip)
24 seal protrusion 24a contact surface 25 end rubber layer 26 outer peripheral rubber layer (hem)
3 Slinger 31 Inner peripheral cylinder part 32 Seal flange 4 Pulsar ring 5 Magnetic sensor G, δ Gap

Claims (2)

外周部材（１１１）の内周面（１１１ａ）に嵌着される外周筒部（１１）を有する取付環（１）と、この取付環（１）に一体的に設けられゴム状弾性材料からなるシールリップ（２２，２３）とを備え、前記外周筒部（１１）の軸方向一部に、その肉厚を内周側へ減少させた薄肉部（１３）が形成され、この薄肉部（１３）の外周面に、ゴム状弾性材料からなり前記外周部材（１１１）の内周面（１１１ａ）に適当なつぶし代（ｈ）をもって密接されるシール突条（２４）を形成してなることを特徴とする密封装置。   An attachment ring (1) having an outer peripheral cylindrical portion (11) fitted to the inner peripheral surface (111a) of the outer peripheral member (111), and a rubber-like elastic material provided integrally with the attachment ring (1). A thin lip portion (13) having a reduced thickness toward the inner peripheral side is formed on a part of the outer peripheral cylindrical portion (11) in the axial direction. The thin lip portion (13) is provided with a seal lip (22, 23). ) Formed on the outer peripheral surface of the outer peripheral member (111) is formed with a sealing ridge (24) that is in close contact with the inner peripheral surface (111a) of the outer peripheral member (111) with an appropriate crushing margin (h). Sealing device characterized. シール突条（２４）の裾部（２６）の外径が、取付環（１）の外周筒部（１１）の外径よりも小径に形成されたことを特徴とする請求項１に記載の密封装置。   The outer diameter of the skirt (26) of the seal protrusion (24) is formed to be smaller than the outer diameter of the outer peripheral cylindrical portion (11) of the mounting ring (1). Sealing device.
JP2004148596A 2004-05-19 2004-05-19 Sealing device Pending JP2005331002A (en)

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Cited By (12)

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Publication number Priority date Publication date Assignee Title
JP2008025600A (en) * 2006-07-18 2008-02-07 Jtekt Corp Bearing sealing device
WO2009157274A1 (en) * 2008-06-25 2009-12-30 内山工業株式会社 Bearing seal
JP2010071456A (en) * 2008-09-22 2010-04-02 Jtekt Corp Bearing device
JP2011080499A (en) * 2009-10-05 2011-04-21 Ntn Corp Wheel bearing device
CN102062214A (en) * 2010-11-25 2011-05-18 青岛开世密封工业有限公司 Spring-free split oil seal resisting muddy water and installation method thereof
JP2012106521A (en) * 2010-11-15 2012-06-07 Jtekt Corp Sealing device and rolling bearing
ITTO20130804A1 (en) * 2013-10-03 2015-04-04 Skf Ab SEALING COMPLEX, IN PARTICULAR FOR ROLLING BEARINGS
ITTO20130799A1 (en) * 2013-10-03 2015-04-04 Skf Ab LOW FRICTION SEALING COMPLEX, IN PARTICULAR FOR ROLLING BEARINGS
JP2017026124A (en) * 2015-07-28 2017-02-02 内山工業株式会社 Seal member
WO2020250579A1 (en) 2019-06-12 2020-12-17 Nok株式会社 Sealing device
CN113924424A (en) * 2019-06-19 2022-01-11 Ntn株式会社 Bearing device for wheel
US20220221005A1 (en) * 2021-01-08 2022-07-14 Aktiebolaget Skf Bearing seat assembly

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JPS558277U (en) * 1978-07-03 1980-01-19
JPH0594575U (en) * 1991-06-12 1993-12-24 内山工業株式会社 Seal fitting structure

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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008025600A (en) * 2006-07-18 2008-02-07 Jtekt Corp Bearing sealing device
CN102066791A (en) * 2008-06-25 2011-05-18 内山工业株式会社 Bearing seal
WO2009157274A1 (en) * 2008-06-25 2009-12-30 内山工業株式会社 Bearing seal
JP2010007712A (en) * 2008-06-25 2010-01-14 Uchiyama Manufacturing Corp Bearing seal
RU2472046C2 (en) * 2008-06-25 2013-01-10 Утияма Мэньюфэкчеринг Корп. Bearing seal
JP2010071456A (en) * 2008-09-22 2010-04-02 Jtekt Corp Bearing device
JP2011080499A (en) * 2009-10-05 2011-04-21 Ntn Corp Wheel bearing device
JP2012106521A (en) * 2010-11-15 2012-06-07 Jtekt Corp Sealing device and rolling bearing
CN102062214A (en) * 2010-11-25 2011-05-18 青岛开世密封工业有限公司 Spring-free split oil seal resisting muddy water and installation method thereof
ITTO20130804A1 (en) * 2013-10-03 2015-04-04 Skf Ab SEALING COMPLEX, IN PARTICULAR FOR ROLLING BEARINGS
ITTO20130799A1 (en) * 2013-10-03 2015-04-04 Skf Ab LOW FRICTION SEALING COMPLEX, IN PARTICULAR FOR ROLLING BEARINGS
JP2017026124A (en) * 2015-07-28 2017-02-02 内山工業株式会社 Seal member
WO2020250579A1 (en) 2019-06-12 2020-12-17 Nok株式会社 Sealing device
US11796004B2 (en) 2019-06-12 2023-10-24 Nok Corporation Sealing device
CN113924424A (en) * 2019-06-19 2022-01-11 Ntn株式会社 Bearing device for wheel
US20220221005A1 (en) * 2021-01-08 2022-07-14 Aktiebolaget Skf Bearing seat assembly
US12006979B2 (en) * 2021-01-08 2024-06-11 Aktiebolaget Skf Bearing seat assembly

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