JP2010185491A - Bearing sealing device - Google Patents

Bearing sealing device Download PDF

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Publication number
JP2010185491A
JP2010185491A JP2009028974A JP2009028974A JP2010185491A JP 2010185491 A JP2010185491 A JP 2010185491A JP 2009028974 A JP2009028974 A JP 2009028974A JP 2009028974 A JP2009028974 A JP 2009028974A JP 2010185491 A JP2010185491 A JP 2010185491A
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Japan
Prior art keywords
sealing device
bearing
fitting cylindrical
bearing sealing
lip
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JP2009028974A
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Japanese (ja)
Inventor
Hirotsugu Seno
洋嗣 勢野
Masanori Shibayama
昌範 柴山
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Uchiyama Manufacturing Corp
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Uchiyama Manufacturing Corp
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Priority to JP2009028974A priority Critical patent/JP2010185491A/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
    • F16C33/7873—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
    • 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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a novel bearing sealing device capable of preventing a radial-directional side slip when piled up, and capable of preventing effectively a grease applied onto an axial lip from being deposited onto the other core bar or the like, by simple structure. <P>SOLUTION: This bearing sealing device 5 includes: the core bar 7 comprising a fitting cylindrical part 71 press-fitted to an outer ring inner circumferential part 2a of a bearing 1, and an inward-directed flange part 73 formed adjacently from one end part 71a of the fitting cylindrical part, and formed to be bent toward a centripetal direction; a lip base part 80 fixed integrally onto an outer face side part ranging over from the one end part to an inner circumferential edge part 73a of the flange shape part including a curved shape portion 72; and the plurality of axial lips 81, etc. formed in the lip base part. The lip base part includes a reception support part 80b for reception-supporting the other end part 71b of the fitting cylindrical part in the adjacent sealing device, when the plurality of the sealing devices is piled up concentrically, a cylindrical wall of the fitting cylindrical part is formed to make a portion from a midway to the other end thin-walled 71c, and the side slip is prevented from being generated in the bearing sealing devices under a piled-up state. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、軸受密封装置に関し、特に、自動車用車輪を回転自在に支持するハブベアリングにおいて、ハブフランジ側に装着される軸受密封装置に関する。   The present invention relates to a bearing sealing device, and more particularly to a bearing sealing device that is mounted on a hub flange side in a hub bearing that rotatably supports automobile wheels.

自動車用車輪は、内輪、外輪及び内外輪間に介在される転動体によって構成される軸受部を介して回転自在に支持される。そして、軸受部はハブベアリングによって構成され、ハブベアリングは、車体側に固定される外輪と、回転（駆動回転或いは従動回転）シャフトに固定され、外輪に対し前記転動体を介して相対回転可能に支持される内輪としてのハブ輪とよりなる。該ハブ輪の一端には、遠心方向に延びるハブフランジが連成され、該ハブフランジにタイヤホイールがボルトによって固定される。前記転動体が介在される軸受空間は、内外輪間に介装された軸受密封装置（シールリング）によって密封され、軸受空間内に装填されたグリース等の潤滑剤の漏出防止や、外部からの汚泥等の浸入の防止が図られている（例えば、特許文献１参照）。   The wheel for motor vehicles is rotatably supported via the bearing part comprised by the rolling element interposed between an inner ring, an outer ring, and an inner and outer ring. The bearing portion is constituted by a hub bearing, and the hub bearing is fixed to an outer ring fixed to the vehicle body side and a rotation (drive rotation or driven rotation) shaft, and can be rotated relative to the outer ring via the rolling element. It consists of a hub ring as an inner ring to be supported. A hub flange extending in the centrifugal direction is coupled to one end of the hub wheel, and a tire wheel is fixed to the hub flange with a bolt. The bearing space in which the rolling element is interposed is sealed by a bearing sealing device (seal ring) interposed between the inner and outer rings to prevent leakage of a lubricant such as grease loaded in the bearing space, and from the outside. Intrusion of sludge and the like is prevented (see, for example, Patent Document 1).

そして、ハブフランジ側の軸受密封装置は、軸受の外輪内周部に圧入嵌合される芯金と、該芯金に一体に固着された弾性体からなるシールリップ部材とよりなり、シールリップ部材は、複数のアキシャルリップを含み、外輪内周部に圧入嵌合された際には、このアキシャルリップがハブ輪のハブフランジに弾接されるよう構成される。この一例を、図６を参照して説明する。図６に示す軸受密封装置（シールリング）１００は、ハブベアリング（不図示）に組込む前で、複数を上下に積重ねた状態を示している。このシールリング１００は、ハブベアリングの外輪内周部に圧入嵌合される芯金１１０と、該芯金１１０に一体に固着された弾性体からなるシールリップ部材１２０とよりなり、前記芯金１１０は、前記外輪内周部に圧入嵌合される嵌合円筒部１１１と、該嵌合円筒部１１１の一端部１１１ａより連成され、湾曲形状部分１１２ａを含んで求心方向に屈曲形成された内向鍔状部１１２とよりなる。   The bearing sealing device on the hub flange side includes a core metal press-fitted into the inner peripheral portion of the outer ring of the bearing, and a seal lip member made of an elastic body integrally fixed to the core metal. Includes a plurality of axial lips, and is configured to be elastically contacted with a hub flange of the hub wheel when the inner ring is press-fitted to the inner periphery of the outer ring. An example of this will be described with reference to FIG. A bearing sealing device (seal ring) 100 shown in FIG. 6 shows a state in which a plurality of bearing sealing devices (seal rings) are stacked in a vertical direction before being assembled into a hub bearing (not shown). The seal ring 100 includes a metal core 110 that is press-fitted into the inner peripheral portion of the outer ring of the hub bearing, and a seal lip member 120 that is formed of an elastic body that is integrally fixed to the metal core 110. Is formed of a fitting cylindrical portion 111 press-fitted to the inner peripheral portion of the outer ring, and one end portion 111a of the fitting cylindrical portion 111, and is inwardly bent in the centripetal direction including the curved portion 112a. It consists of a bowl-shaped part 112.

また、前記シールリップ部材１２０は、前記一端部１１１ａから前記湾曲形状部分１１２ａを含む前記鍔状部１１２の内周縁部１１２ｂに亘る外面側部１１２ｃに一体に固着されたリップ基部１２１と、該リップ基部１２１より遠心方向に拡径するよう同心円錐状に形成された複数のアキシャルリップ１２２，１２３とを備えている。更に、図示のシールリップ部材１２０は、１個のラジアルリップ１２４を備えている。また、リップ基部１２１の、前記一端部１１１ａの近傍部位には、嵌合円筒部１１１の外周部より外方に突出するよう形成された環状突部（ノーズ部）１２１ａが形成され、この環状突部１２１ａから前記湾曲形状部分１１２ａの外面を覆ってアキシャルリップ１２２の根元部に至る部分は、本軸受密封装置１００を、治具（不図示）によって外輪内周部に圧入嵌合する際の治具の作用部１２１ｂとされる。   The seal lip member 120 includes a lip base 121 integrally fixed to an outer surface side portion 112c extending from the one end portion 111a to an inner peripheral edge portion 112b of the flange-like portion 112 including the curved portion 112a, and the lip A plurality of axial lips 122 and 123 formed concentrically conically so as to expand in the centrifugal direction from the base 121. Further, the illustrated seal lip member 120 includes one radial lip 124. In addition, an annular protrusion (a nose portion) 121a formed so as to protrude outward from the outer peripheral portion of the fitting cylindrical portion 111 is formed in a portion of the lip base 121 near the one end portion 111a. The portion from the portion 121a to the base portion of the axial lip 122 that covers the outer surface of the curved portion 112a is treated when the bearing sealing device 100 is press-fitted and fitted to the inner peripheral portion of the outer ring with a jig (not shown). The action part 121b of the tool is used.

特開２００７−１２７２０３号公報JP 2007-127203 A

図６に示すようなシールリング（軸受密封装置）１００は、ハブベアリング（図１及び図２参照）に装着されるが、ハブベアリングの組立工程（組立工場）に至るまでは、図６に示すように複数を同心的に積重ねた状態で梱包され、搬送及び搬入される。このとき、前記アキシャルリップ１２２，１２３の先側内周部にはグリースＧ１，Ｇ２が塗布されるが、これらグリースＧ１，Ｇ２は、ハブベアリングの組立工程の効率化を図る為に、梱包段階で事前に塗布されている。そして、複数のシールリング１００は、各芯金１１０における嵌合円筒部１１１の他端部１１１ｂを、前記リップ基部１２１の各作用部１２１ｂの上に載せるようにして、順次積重ねられる。このような積重ね状態では、前記搬送過程等において、各シールリング１００が径方向に横ずれし、アキシャルリップ１２２，１２３に塗布されたグリースＧ１，Ｇ２が、上積みされるシールリング１００の芯金１１０における鍔状内向鍔状部１１２の内面側部１１２ｄに付着する。このように、グリースＧ１，Ｇ２が上積みされたシールリング１００に付着すると、シール性や摺動性等の観点から設計された所定のグリース量が減り、密封装置としての所期の意図する性能が得られなく事態が生じる。   A seal ring (bearing sealing device) 100 as shown in FIG. 6 is mounted on a hub bearing (see FIGS. 1 and 2), but it is shown in FIG. 6 until the hub bearing assembly process (assembly factory). Thus, a plurality of products are packed in a concentrically stacked state, transported and carried in. At this time, greases G1 and G2 are applied to the inner peripheral portions on the front side of the axial lips 122 and 123. These greases G1 and G2 are used at the packing stage in order to improve the efficiency of the hub bearing assembly process. Applied in advance. The plurality of seal rings 100 are sequentially stacked such that the other end portion 111 b of the fitting cylindrical portion 111 of each core metal 110 is placed on each action portion 121 b of the lip base 121. In such a stacked state, in the conveying process or the like, each seal ring 100 is laterally displaced in the radial direction, and the greases G1 and G2 applied to the axial lips 122 and 123 are in the core metal 110 of the seal ring 100 to be stacked. It adheres to the inner surface side portion 112d of the hook-shaped inward hook-like portion 112. As described above, when the grease G1 and G2 adhere to the stacked seal ring 100, the predetermined amount of grease designed from the viewpoints of sealability and slidability is reduced, and the intended performance as a sealing device is reduced. Things get out of hand.

因みに、ハブベリング用のシールリングの場合、ハブ輪からハブフランジに至る凹曲面部に対して弾接する複数のシールリップの形成スペースを確保する為、図示のように、嵌合円筒部１１１に連成される内向鍔状部１１２が、湾曲形状部分１１２ａを含んで屈曲形成された形状とされることが多い。その為、図のように複数の軸受密封装置１００を積重ねた際、特に、アキシャルリップ１２２の先側部が、前記湾曲形状部分１１２ａの内面凹曲空間部分に入り込むような形状とならざるを得ず、軸受密封装置１００が互いに径方向に少しでも横ずれした場合、このアキシャルリップ１２２に塗布されたグリースＧ１が、上積みされるシールリング１００の芯金１１０に付着し易くなる。また、ラジアルリップ１２４の形成態様によっては、アキシャルリップ１２３に塗布されたグリースＧ２が、ラジアルリップ１２４或いはその形成基部等に付着することもある。   Incidentally, in the case of a seal ring for hub belling, in order to secure a space for forming a plurality of seal lips that elastically contact the concave curved surface portion from the hub wheel to the hub flange, it is coupled to the fitting cylindrical portion 111 as shown in the figure. The inwardly saddle-like portion 112 to be bent is often formed to be bent including the curved portion 112a. Therefore, when a plurality of bearing sealing devices 100 are stacked as shown in the figure, the tip side portion of the axial lip 122 must be shaped so as to enter the inner concave space portion of the curved portion 112a. If the bearing sealing device 100 is slightly displaced in the radial direction, the grease G1 applied to the axial lip 122 is likely to adhere to the core metal 110 of the seal ring 100 to be stacked. Further, depending on the form of formation of the radial lip 124, the grease G2 applied to the axial lip 123 may adhere to the radial lip 124 or its forming base.

特許文献１は、前記のようなグリースの付着を防止する為、シールリップ（アキシャルリップ）に塗布したグリースの表面と、隣接する密封装置との間に所要の隙間を保持する保持部を基部ゴム層（リップ基部）に設けている。このような保持部としては、突起や環状段差が例示されている。しかし、本特許文献１で例示される保持部は、軸受外輪の内周部に圧入嵌合させる際に治具を作用させる部位に形成される為、この作用部位が狭められることになり、治具による圧入嵌合の作業性が低下することが予想されるところであった。また、このような、保持部を基部ゴム層に設ける場合、シールリップ部材の成型用金型の構造が複雑となり、コストアップの原因の１つになることは否めなかった。   In Patent Document 1, in order to prevent the adhesion of the grease as described above, a base rubber is provided with a holding portion that holds a required gap between the surface of the grease applied to the seal lip (axial lip) and the adjacent sealing device. It is provided on the layer (lip base). As such a holding part, a protrusion and an annular step are illustrated. However, since the holding portion exemplified in Patent Document 1 is formed at a portion where a jig acts when press-fitted to the inner peripheral portion of the bearing outer ring, this acting portion will be narrowed, and the healing portion will be reduced. It was expected that the workability of the press fitting with the tool would be lowered. Further, when such a holding portion is provided on the base rubber layer, the structure of the mold for molding the seal lip member becomes complicated, and it cannot be denied that this is one of the causes of cost increase.

本発明は、前記実情に鑑みなされたものであり、簡単な構造でありながら、積重ねた際の径方向の相互の横ずれを防止し、アキシャルリップに塗布されたグリースが、他方の芯金等に付着することを有効に防止することができる新規な軸受密封装置を提供することを目的としている。   The present invention has been made in view of the above circumstances, and while having a simple structure, prevents lateral displacement in the radial direction when stacked, and the grease applied to the axial lip is applied to the other core metal or the like. An object of the present invention is to provide a novel bearing sealing device capable of effectively preventing adhesion.

本発明に係る軸受密封装置は、芯金と、該芯金に一体に固着された弾性体からなるシールリップ部材とよりなる軸受密封装置であって、前記芯金は、軸受外輪に嵌合一体とされる嵌合円筒部と、該嵌合円筒部の一端部より連成され、湾曲形状部分を含んで求心方向に屈曲形成された内向鍔状部とよりなり、前記シールリップ部材は、前記一端部から前記湾曲形状部分を含む前記鍔状部の内周縁部に亘る外面側部に一体に固着されたリップ基部と、該リップ基部より遠心方向に拡径するよう同心円錐状に形成された複数のアキシャルリップとを備え、前記リップ基部は、当該軸受密封装置の複数を同心的に積重ねた際、隣接密封装置における前記嵌合円筒部の他端部を受支する受支部を含み、前記嵌合円筒部の筒壁は、途中から前記他端部に至る部分が薄肉に形成されていることを特徴とする。   A bearing sealing device according to the present invention is a bearing sealing device including a cored bar and a seal lip member made of an elastic body integrally fixed to the cored bar, and the cored bar is integrally fitted with a bearing outer ring. A fitting cylindrical portion, and an inward flanged portion formed in a centripetal direction including a curved portion, the sealing lip member including the curved cylindrical portion, A lip base integrally fixed to an outer surface side portion extending from one end portion to the inner peripheral edge of the bowl-shaped portion including the curved portion, and a conical conical shape so as to expand in the centrifugal direction from the lip base. A plurality of axial lips, and the lip base includes a receiving portion that receives and supports the other end portion of the fitting cylindrical portion in the adjacent sealing device when the plurality of the bearing sealing devices are concentrically stacked. The cylindrical wall of the fitting cylindrical part reaches the other end partway from the middle. Portion is characterized in that it is formed thin.

本発明において、前記受支部としては、粗面化処理による高摩擦係数化処理面からなるもの、前記嵌合円筒部の他端部を傾斜面で受支するべく該嵌合円筒部と同心に形成された環状テーパー形状部からなるもの、更には、前記嵌合円筒部の他端部を嵌受するべく該嵌合円筒部と同心に形成された環状凹溝部からなるもの、等であっても良い。加えて、前記嵌合円筒部の他端部の断面形状を先細状としても良い。高摩擦係数化処理面は、前記粗面化処理によって形成することができ、この粗面化処理の方法としては、ショットブラスト法等が望ましく採用される。   In the present invention, the receiving part is composed of a surface having a high coefficient of friction treatment by roughening treatment, and is concentric with the fitting cylindrical part so as to receive the other end of the fitting cylindrical part with an inclined surface. It is formed of an annular tapered portion formed, and further is formed of an annular groove formed concentrically with the fitting cylindrical portion so as to receive the other end of the fitting cylindrical portion. Also good. In addition, the cross-sectional shape of the other end portion of the fitting cylindrical portion may be tapered. The surface having a high friction coefficient treatment can be formed by the roughening treatment, and a shot blasting method or the like is preferably employed as the roughening treatment method.

本発明において、本発明の軸受密封装置をハブベアリング用の密封装置とし、前記芯金をしてハブベアリングの外輪内周部に圧入嵌合された状態では、前記アキシャルリップの先側がハブ輪のハブフランジに弾接されるよう構成されているものとすることができる。   In the present invention, the bearing sealing device of the present invention is a sealing device for a hub bearing, and in the state where the cored bar is press-fitted to the inner peripheral portion of the outer ring of the hub bearing, the front side of the axial lip is the hub ring. It may be configured to be elastically contacted with the hub flange.

本発明に係る軸受密封装置は、芯金の嵌合円筒部をして、軸受の外輪に嵌合されて、外輪に一体化される。軸受がハブベアリングである場合には、前記複数のアキシャルリップの先側がハブ輪のハブフランジに弾接される。従って、回転側の内輪としてのハブ輪と外輪との間の軸受空間が、アキシャルリップのハブフランジに対する弾性摺接によりシールされ、軸受空間内への外部からの汚泥や塵埃等の侵入が防止され、また、軸受空間内に充填されたグリース等の潤滑剤の外部への漏出が防止される。各アキシャルリップの先側内周部にグリースが塗布されている場合は、前記弾接部分にグリースが介在され、アキシャルリップの前記弾性摺接時の低トルク化が図られると共に、弾性摺接部のシール性も維持される。そして、このグリースは事前に塗布された状態で軸受の組立てに供されるから、軸受組立工程の効率化が図られる。   The bearing sealing device according to the present invention has a fitting cylindrical portion of a metal core, is fitted to the outer ring of the bearing, and is integrated with the outer ring. When the bearing is a hub bearing, the front sides of the plurality of axial lips are elastically contacted with the hub flange of the hub wheel. Therefore, the bearing space between the hub ring as the inner ring on the rotating side and the outer ring is sealed by elastic sliding contact with the hub flange of the axial lip, and entry of sludge, dust, etc. from the outside into the bearing space is prevented. In addition, leakage of lubricant such as grease filled in the bearing space to the outside is prevented. When grease is applied to the front inner peripheral portion of each axial lip, the grease is interposed in the elastic contact portion to reduce the torque during the elastic sliding contact of the axial lip, and the elastic sliding contact portion The sealing performance is also maintained. And since this grease is used for the assembly of a bearing in the state apply | coated previously, the efficiency of a bearing assembly process is achieved.

そして、本発明の軸受密封装置は、前述のように、複数のアキシャルリップの先側内周部にグリースが塗布され、このグリースが隣接軸受密封装置に付着しない状態で、複数が同心的に積重ねられて前記組立工程に持ち込まれることが多い。この輸送過程等においては、当該軸受密封装置に対して径方向に相互に横ずれするような外力が作用する。而して、前記受支部によって受支される隣接軸受密封装置の前記他端部が、薄肉に形成された嵌合円筒部の筒壁の先端部となるから、前記積重ね状態ではその荷重が付加され、弾性体からなるシールリップ部材のリップ基部に食い込み、相互の横ずれが阻止される。従って、前記事前に塗布されたグリースが、当該隣接軸受密封装置の前記芯金等に付着することがなく、事前に塗布された所定量のグリースが減ることがない。これにより、所期の意図する前記性能が得られなくなるような事態が生じる懸念がない。   In the bearing sealing device of the present invention, as described above, the grease is applied to the front inner peripheral portions of the plurality of axial lips, and a plurality of them are concentrically stacked in a state where the grease does not adhere to the adjacent bearing sealing device. In many cases, it is brought into the assembly process. In this transportation process or the like, an external force that is laterally displaced in the radial direction acts on the bearing sealing device. Thus, the other end portion of the adjacent bearing sealing device supported by the receiving portion becomes the tip portion of the cylindrical wall of the fitting cylindrical portion formed thin, so that the load is applied in the stacked state. Then, it bites into the lip base portion of the seal lip member made of an elastic body, and mutual lateral displacement is prevented. Accordingly, the pre-applied grease does not adhere to the cored bar or the like of the adjacent bearing sealing device, and the predetermined amount of pre-applied grease does not decrease. As a result, there is no concern that a situation in which the intended performance cannot be obtained.

前記受支部を、粗面化処理による高摩擦係数化処理面からなるものとした場合、この受支部と嵌合円筒部の他端部との摩擦抵抗と、前記他端部の受支部に対する食い込み機能とが相俟って、前記相互の横ずれの阻止がより確実になされ、隣接軸受密封装置にグリースが付着する事態がより生じ難くなる。また、前記受支部を、前記嵌合円筒部の他端部を傾斜面で受支するべく該嵌合円筒部と同心に形成された環状テーパー形状部からなるものとした場合、積重なった当該軸受密封装置の荷重が加わって、互いに楔合するような嵌合関係の受支状態となり、同心的な積重ね状態が安定し、相互の横ずれの阻止がより確実になされる。更に、前記受支部を、前記嵌合円筒部の他端部を嵌受するべく該嵌合円筒部と同心に形成された環状凹溝部からなるものとした場合、他端部がこの環状凹溝部に嵌まり込むよう受支されるから、同様に同心的な積重ね状態が安定し、相互の横ずれの阻止がより確実になされる。そして、前記嵌合円筒部の他端部の断面形状を先細状とした場合、該他端部の前記受支部に対する食い込み機能がより顕著になり、同様に同心的な積重ね状態が安定する。   When the receiving part is made of a surface with a high friction coefficient by roughening, the frictional resistance between the receiving part and the other end of the fitting cylindrical part, and the biting of the other end with respect to the receiving part Combined with the function, the mutual lateral displacement is more reliably prevented, and a situation where grease adheres to the adjacent bearing sealing device is less likely to occur. Further, when the receiving portion is formed of an annular tapered portion formed concentrically with the fitting cylindrical portion so as to receive the other end portion of the fitting cylindrical portion with an inclined surface, The load of the bearing sealing device is applied, and the receiving state is in a fitting relationship such that they are wedged together, the concentric stacking state is stabilized, and mutual lateral displacement is more reliably prevented. Furthermore, when the said support part consists of an annular groove part formed concentrically with this fitting cylinder part so that the other end part of the said fitting cylinder part may be received, the other end part is this annular groove part. Therefore, the concentric stacked state is similarly stabilized, and the mutual lateral displacement is more reliably prevented. And when the cross-sectional shape of the other end part of the said fitting cylindrical part is made into a taper shape, the biting function with respect to the said receiving part of this other end part becomes more remarkable, and a concentric stacking state is stabilized similarly.

本発明の一実施形態の軸受密封装置を組み込んだ軸受の一例を示す縦断面図である。It is a longitudinal section showing an example of a bearing incorporating a bearing sealing device of one embodiment of the present invention. 図１におけるＸ部の拡大図である。It is an enlarged view of the X section in FIG. 同軸受密封装置を積重ねた状態の断面図である。It is sectional drawing of the state which accumulated the bearing sealing device. 他の実施形態の軸受密封装置の断面図である。It is sectional drawing of the bearing sealing device of other embodiment. 更に他の実施形態の軸受密封装置の断面図である。It is sectional drawing of the bearing sealing device of other embodiment. 従来の軸受密封装置を積重ねた状態の断面図である。It is sectional drawing of the state which accumulated the conventional bearing sealing device.

以下に本発明の最良の実施の形態について、図面に基づいて説明する。図１は自動車の車輪を回転自在に支持するハブベアリング（軸受）１の構造の一例を示すものであり、外輪２は、車体の懸架装置（不図示）に取付固定される。内輪３を構成するハブ輪３Ａのハブフランジ３ａにボルト３ｂによりタイヤホイール（不図示）が固定される。また、ハブ輪３Ａに形成されたスプライン軸孔３ｃには駆動シャフト（不図示）がスプライン嵌合されて、該駆動シャフトの回転駆動力がタイヤホイールに駆動伝達される。そして、ハブ輪３Ａは内輪部材３Ｂと共に内輪３を構成する。この外輪２と前記内輪３との間に２列の転動体（玉）４…がリテーナ４ａで保持された状態で介装されている。この転動体４…及び内外輪２，３に形成された各軌道面により軸受空間１Ａが構成され、軸受空間１Ａを介して、内輪３が外輪２に対して軸回転可能に支持される。前記シャフトが従動回転するものである場合は、該シャフトは、ハブ輪３Ａと共に外輪２に対してフリー回転可能とされる。２列の転動体（玉）４…の軌道面の軸心Ｌ方向に沿った外側、即ち、前記軸受空間１Ａの軸心Ｌ方向の両側には、前記転動体４…の転動部（軸受空間１Ａ）に装填される潤滑剤（グリース）の漏出或いは外部からの汚泥等の浸入を防止するためのシールリング（軸受密封装置）５，６が、外輪２と内輪３との間に圧入装着されている。   The best mode for carrying out the present invention will be described below with reference to the drawings. FIG. 1 shows an example of the structure of a hub bearing (bearing) 1 that rotatably supports the wheels of an automobile, and an outer ring 2 is attached and fixed to a suspension device (not shown) of a vehicle body. A tire wheel (not shown) is fixed to the hub flange 3a of the hub ring 3A constituting the inner ring 3 by bolts 3b. A drive shaft (not shown) is spline-fitted into the spline shaft hole 3c formed in the hub wheel 3A, and the rotational driving force of the drive shaft is transmitted to the tire wheel. The hub wheel 3A constitutes the inner ring 3 together with the inner ring member 3B. Two rows of rolling elements (balls) 4... Are interposed between the outer ring 2 and the inner ring 3 while being held by a retainer 4a. A bearing space 1A is constituted by the raceways formed on the rolling elements 4 and the inner and outer rings 2 and 3, and the inner ring 3 is supported by the outer ring 2 so as to be axially rotatable via the bearing space 1A. When the shaft rotates in a driven manner, the shaft can be freely rotated with respect to the outer ring 2 together with the hub wheel 3A. On the outer side of the raceway surface of the two rows of rolling elements (balls) 4 along the axis L direction, that is, on both sides of the bearing space 1A in the axis L direction, the rolling parts (bearings) of the rolling elements 4. Seal rings (bearing sealing devices) 5 and 6 are press-fitted between the outer ring 2 and the inner ring 3 to prevent leakage of lubricant (grease) loaded in the space 1A) or entry of sludge from the outside. Has been.

図２は、反車体側（アウター側）シールリング５の装着部の拡大断面図を示し、図３をも参照してシールリング５の構造を説明する。該シールリング５は、外輪２の内周部に圧入嵌合一体に装着される芯金７と、該芯金７に固着一体とされ３個のシールリップ８１，８２，８３を備えるシールリップ部材８とよりなる。芯金７は、前記外輪２の内周部２ａに圧入嵌合される嵌合円筒部７１と、該嵌合円筒部７１の一端部７１ａより連成され、湾曲形状部分７２を含んで求心方向に屈曲形成された内向鍔状部７３とよりなる。嵌合円筒部７１の筒壁は、途中から他端部７１ｂに至る部分が薄肉（以下、薄肉部分と言う）７１ｃに形成されている。この薄肉部分７１ｃは、嵌合円筒部７１の筒壁の内径が、途中から段差状に径大化した状態で形成されている。また、薄肉部分７１ｃの先端となる他端部７１ｂは、その断面形状が先細状に形成されている。   FIG. 2 is an enlarged cross-sectional view of the mounting portion of the non-vehicle body side (outer side) seal ring 5, and the structure of the seal ring 5 will be described with reference to FIG. The seal ring 5 is a seal lip member that includes a cored bar 7 that is press-fitted and fitted integrally to the inner peripheral portion of the outer ring 2, and three seal lips 81, 82, and 83 that are integrally fixed to the cored bar 7. 8 and so on. The metal core 7 is formed of a fitting cylindrical portion 71 press-fitted to the inner peripheral portion 2 a of the outer ring 2 and one end portion 71 a of the fitting cylindrical portion 71, and includes a curved portion 72 and a centripetal direction. And an inwardly saddle-shaped portion 73 that is bent. The cylindrical wall of the fitting cylindrical portion 71 has a thin portion (hereinafter referred to as a thin portion) 71c that extends from the middle to the other end portion 71b. The thin portion 71c is formed in a state where the inner diameter of the cylindrical wall of the fitting cylindrical portion 71 is increased in a stepped shape from the middle. Further, the other end portion 71b which is the tip of the thin portion 71c has a tapered cross section.

また、前記シールリップ部材８は、前記芯金７の一端部７１ａから前記湾曲形状部分７２を含む前記鍔状部７３の内周縁部７３ａに亘る外面側部７３ｂに一体に固着されたリップ基部８０と、前記３個のシールリップ８１，８２，８３とよりなる。図示のシールリップ部材８はゴムの成型体からなり、ゴム材の芯金７に対する加硫一体成型により形成したものを示している。該リップ基部８０は、前記内向鍔状部７３の内周縁部７３ａを回り込むように固着一体とされている。シールリップ８３は、ラジアルリップ（グリースリップ）であり、前記内周縁部７３ａを回り込む部分より前記軸受空間１Ａ側に向かい求心方向に縮径するよう、前記軸心Ｌを中心とする円錐状に形成されている。シールリップ８１，８２は、アキシャルリップであり、前記リップ基部８０より前記軸受空間１Ａとは反対側に向かい遠心方向に拡径するよう、前記軸心Ｌを中心とする同心円錐状に形成されている。   The seal lip member 8 is integrally fixed to an outer surface side portion 73b extending from one end portion 71a of the cored bar 7 to the inner peripheral edge portion 73a of the flange-shaped portion 73 including the curved portion 72. And the three sealing lips 81, 82, 83. The illustrated seal lip member 8 is made of a rubber molded body and is formed by vulcanization integral molding of a rubber core metal 7. The lip base portion 80 is integrally fixed so as to go around the inner peripheral edge portion 73a of the inwardly saddle-like portion 73. The seal lip 83 is a radial lip (grease lip), and is formed in a conical shape with the shaft center L as the center so that the diameter of the seal lip 83 decreases toward the bearing space 1 </ b> A from the portion around the inner peripheral edge 73 a. Has been. The seal lips 81 and 82 are axial lips, and are formed in a conical conical shape with the shaft center L as the center so as to expand in the centrifugal direction from the lip base 80 toward the opposite side to the bearing space 1A. Yes.

前記リップ基部８０の前記一端部７１ａの近傍部位には、嵌合円筒部７１の外周部より外方に突出するよう形成された環状突部（ノーズ部）８４が形成されている。この環状突部８４から前記湾曲形状部分７２の外面を覆って前記最外周側のアキシャルリップ８１の根元部に至る部分は、シールリング５を、白抜矢印に示すように治具（不図示）を作用させることによって、外輪２の内周部２ａに圧入嵌合する際の治具の作用部８０ａとされる。この作用部８０ａの表面は、前記治具の作用力ができるだけ均等に作用するよう平坦面とされるが、この作用部８０ａの外周側部分は、後記する積重ねの際における嵌合円筒部７１の他端部７１ｂを受支する受支部８０ｂとされる。図例では、この受支部８０ｂの表面はショットブラスト法等の粗面化処理により形成された細かな凹凸面からなる高摩擦係数化処理面とされているが、ゴムの材質が高摩擦係数のものであれば、このような粗面化処理を特に施さなくても良い。   An annular protrusion (nose portion) 84 formed so as to protrude outward from the outer peripheral portion of the fitting cylindrical portion 71 is formed in the vicinity of the one end portion 71 a of the lip base portion 80. A portion of the annular protrusion 84 that covers the outer surface of the curved portion 72 and reaches the root of the outermost axial lip 81 has a seal ring 5 as a jig (not shown). By acting, the action portion 80a of the jig when press-fitting to the inner peripheral portion 2a of the outer ring 2 is obtained. The surface of the action portion 80a is a flat surface so that the action force of the jig acts as evenly as possible, but the outer peripheral side portion of the action portion 80a is formed by the fitting cylindrical portion 71 in the stacking described later. A receiving portion 80b that receives and supports the other end portion 71b is provided. In the example shown in the drawing, the surface of the support portion 80b is a surface with a high coefficient of friction made of a fine uneven surface formed by a roughening process such as a shot blasting method, but the rubber material has a high coefficient of friction. If it is a thing, it is not necessary to give such a roughening process in particular.

前記圧入嵌合により、前記環状突部８４が外輪２の内周部２ａと前記小径円筒部７２ａの外周部との間に圧縮弾性変形状態で挟圧され、この復元弾力による相互の面圧によって、外輪２とシールリング５との間の良好な密封性が維持される。そして、図例では、嵌合円筒部７１の一端部７１ａから湾曲形状部７２に連なる部分は漸次縮径状とされているから、この部分が前記環状突部８４の圧縮弾性変形時の逃げ部とされ、前記圧入嵌合時の抵抗が緩和される。   Due to the press-fitting, the annular protrusion 84 is sandwiched between the inner peripheral portion 2a of the outer ring 2 and the outer peripheral portion of the small-diameter cylindrical portion 72a in a state of compressive elastic deformation, and due to mutual surface pressure due to this restoring elasticity The good sealing performance between the outer ring 2 and the seal ring 5 is maintained. In the illustrated example, the portion of the fitting cylindrical portion 71 that continues from the one end portion 71a to the curved shape portion 72 is gradually reduced in diameter, so this portion is a relief portion when the annular protrusion 84 is compressed and elastically deformed. Thus, the resistance during the press-fitting is alleviated.

上記構造のシールリング５は、複数が図３に示すように積重ねられて梱包され、ハブベアリング１の組立現場（不図示）に搬入される。図３では、便宜上２個を積重ねた例を示しているが、実際には、１０個単位、２０個単位或は１ダース単位等で積重ね梱包されるものであり、積重ね個数は、搬送性やユーザー側の要望等により適宜定められる。そして、この積重ねの際に、アキシャルリップ８１，８２及びラジアルリップ８３の各先側内周部には、所定量のグリースＧ１，Ｇ２，Ｇ３が事前に塗布される。塗布されたグリースＧ１，Ｇ２，Ｇ３の層厚は、経験的に略一定とされ、上部のシールリング５に付着しないよう設計される。前記組立現場に搬入された梱包体は、開梱され、シールリング５が１個ずつばらされて、前述のように治具を用いて、芯金７の嵌合円筒部７１をして、外輪２の内周部２ａに圧入嵌合される。そして、ハブ輪３Ａが所定の部位に嵌合され、この嵌合によって、図２に示すように、アキシャルリップ８１，８２が弾性変形して、グリースＧ１，Ｇ２を介した状態でハブ輪３Ａのハブフランジ３ａに弾接し、また、ラジアルリップ８３も弾性変形して、グリースＧ３を介した状態でハブ輪３Ａのラジアル面に弾接する。   A plurality of seal rings 5 having the above structure are stacked and packaged as shown in FIG. 3, and are carried into an assembly site (not shown) of the hub bearing 1. FIG. 3 shows an example in which two are stacked for convenience, but in actuality, they are packed in units of 10 units, 20 units, or a dozen units, etc. It is determined appropriately according to the user's request. Then, at the time of this stacking, a predetermined amount of grease G1, G2, G3 is applied in advance to the respective inner peripheral portions of the axial lips 81, 82 and the radial lip 83. The thickness of the applied grease G1, G2, G3 is empirically set to be substantially constant, and is designed not to adhere to the upper seal ring 5. The package carried into the assembly site is unpacked, the seal rings 5 are separated one by one, and the fitting cylinder portion 71 of the cored bar 7 is formed using the jig as described above, and the outer ring 2 is press-fitted into the inner peripheral portion 2a. Then, the hub wheel 3A is fitted into a predetermined part, and by this fitting, the axial lips 81 and 82 are elastically deformed as shown in FIG. Further, the radial lip 83 is elastically deformed and elastically contacts the radial surface of the hub wheel 3A through the grease G3.

図１のように組立てられたハブベアリング１の使用状態においては、外輪２に対してハブ輪３Ａ（内輪３）が軸心Ｌ周りに回転する。この回転に伴い、前記アキシャルリップ８１，８２及びラジアルリップ８３は、ハブ輪３Ａ及びハブフランジ３ａの表面に弾性摺接する。従って、この弾性摺接部分で密封性が維持され、軸受空間１Ａが密封され、軸受空間１Ａ内への汚泥や塵埃の侵入、及び、軸受空間１Ａ内に装填されたグリース（不図示）の外部への漏出が阻止される。また、この弾性摺接部分には、前記グリースＧ１，Ｇ２，Ｇ３が介在されるから、その潤滑作用によって前記弾性摺接を伴ったハブ輪３Ａの軸回転が円滑になされると共に、この弾性摺接部分の密封性もより向上する。   In the use state of the hub bearing 1 assembled as shown in FIG. 1, the hub ring 3 </ b> A (inner ring 3) rotates around the axis L with respect to the outer ring 2. Along with this rotation, the axial lips 81 and 82 and the radial lip 83 come into elastic sliding contact with the surfaces of the hub wheel 3A and the hub flange 3a. Therefore, sealing performance is maintained at this elastic sliding contact portion, the bearing space 1A is sealed, sludge and dust enter the bearing space 1A, and the outside of grease (not shown) loaded in the bearing space 1A. Leakage to is prevented. Further, since the grease G1, G2, G3 is interposed in the elastic sliding contact portion, the hub ring 3A accompanied by the elastic sliding contact is smoothly rotated by the lubricating action, and the elastic sliding contact is made. The sealability of the contact portion is further improved.

前記構成のシールリング５は、図３に示すように複数が上下方向に積重ねられる。この時、下部のシールリング５における前記リップ基部８０の受支部８０ｂに対して、上部のシールリング５における前記嵌合円筒部１１の他端部（下端部）７１ｂを載せ置くようにして、順次同心的に積重ねられる。この積重ね状態では、下部のシールリング５におけるグリースＧ１，Ｇ２，Ｇ３が塗布された状態の各アキシャルリップ８１、８２及びラジアルアリップ８３と、上部の芯金７の内面（下面）とは互いに干渉しないよう設計される。即ち、塗布されたグリースＧ１，Ｇ２，Ｇ３は上部のシールリング５のいずれの部位にも接触することがないよう設計される。また、最外周側のアキシャルリップ８１の先側部は、上部シールリング５における前記湾曲形状部７２の上向き凹湾曲部内に入り込むよう設計され、これにより、積重ね嵩を低くすることができる。また、湾曲形状部７２の形成により、前記ハブ輪３Ａからハブフランジ３ａに至る凹曲面部に対して弾接するアキシャルリップ８１，８２の形成スペースを確保し易く、設計自由度が向上すると共に、リブ効果により芯金７が補強され、前記治具による圧入嵌合の際の耐座屈強度が高められる。   As shown in FIG. 3, a plurality of the seal rings 5 having the above-described configuration are stacked in the vertical direction. At this time, the other end portion (lower end portion) 71b of the fitting cylindrical portion 11 in the upper seal ring 5 is placed on the support portion 80b of the lip base portion 80 in the lower seal ring 5 in order. Stacked concentrically. In this stacked state, the axial lips 81 and 82 and the radial lip 83 in the state where the grease G1, G2, and G3 are applied to the lower seal ring 5 and the inner surface (lower surface) of the upper cored bar 7 interfere with each other. Designed not to. That is, the applied greases G1, G2, G3 are designed not to contact any part of the upper seal ring 5. Further, the front side portion of the outermost axial lip 81 is designed to enter the upward concave curved portion of the curved shape portion 72 in the upper seal ring 5, thereby reducing the stacking bulk. Further, the formation of the curved portion 72 makes it easy to secure a space for forming the axial lips 81 and 82 that are in elastic contact with the concave curved surface portion from the hub wheel 3A to the hub flange 3a. The core metal 7 is reinforced by the effect, and the buckling resistance at the time of press-fitting by the jig is increased.

そして、上部のシールリング５の前記他端部７１ｂは、前記薄肉部分７１ｃの先端部とされ、しかも、先細状に形成されているから、下部のシールリング５に対し、上部のシールリング５の荷重が加わり、ゴム弾性を有する受支部８０ｂの表面に食い込むように載せ置かれる。その為、このような積重ね状態で輸送する際等において、振動等の外力が径方向に作用しても、他端部７１ｂの受支部８０ｂに対する食い込みによって、積重ねられた複数のシールリング５の相互間の横ずれが抑止される。特に、図例では、受支部８０ｂが高摩擦係数化処理面からなるから、これによる相互の摩擦抵抗と、前記食い込みによる作用とが相俟って、一層シールリング５の相互間の横ずれ抑止が効果的になされる。これによって、下部のシールリング５における前記アキシャルリップ８１，８２及びラジアルリップ８３に塗布されたグリースＧ１，Ｇ２，Ｇ３が、隣接する上部のシールリング５の下面部（芯金７の内面側部やラジアルリップ８３）に付着することがない。従って、グリースＧ１，Ｇ２，Ｇ３の所期の塗布量が維持された状態でハブベアリング１に対する組付けがなされ、意図したグリースＧ１，Ｇ２，Ｇ３の前記性能が充分に発揮される。
図３の拡大部では、前記食い込み状態、及び、高摩擦係数化処理面の形成状態を概念的に示している。 The other end 71b of the upper seal ring 5 is the tip of the thin portion 71c, and is formed in a tapered shape, so that the upper seal ring 5 has a lower end than the lower seal ring 5. A load is applied, and the material is placed so as to bite into the surface of the support portion 80b having rubber elasticity. For this reason, even when an external force such as vibration acts in the radial direction when transporting in such a stacked state, the plurality of stacked seal rings 5 are interleaved by biting into the receiving portion 80b of the other end portion 71b. The lateral shift is suppressed. In particular, in the illustrated example, since the support portion 80b is made of a surface with a high friction coefficient, the mutual frictional resistance due to this and the effect of the biting are combined to further suppress the lateral displacement between the seal rings 5. Effectively done. As a result, the greases G1, G2, and G3 applied to the axial lips 81 and 82 and the radial lip 83 in the lower seal ring 5 are applied to the lower surface portion of the adjacent upper seal ring 5 (the inner surface side portion of the core metal 7 and the like). It does not adhere to the radial lip 83). Therefore, the assembly to the hub bearing 1 is performed in a state where the desired application amounts of the greases G1, G2, and G3 are maintained, and the performances of the intended greases G1, G2, and G3 are sufficiently exhibited.
The enlarged portion of FIG. 3 conceptually shows the biting state and the formation state of the high friction coefficient treatment surface.

図４は、他の実施形態を示し、前記シールップ部材８における治具の作用部８０ａの外周側部分に、嵌合円筒部７１に向かい漸次拡径する環状テーパー形状部８０ｃが形成され、この環状テーパー形状部８０ｃが、その傾斜面（テーパー面）によって前記嵌合円筒部７１の他端部７１ｂを受支する受支部とされている。該受支部（環状テーパー形状部）８０ｃは、嵌合円筒部７１と同心的に形成されており、積重ね状態の各上部のシールリング５における嵌合円筒部７１の下端部７１ｂは、受支部８０ｃにおけるテーパー面で食い込むように受支される。   FIG. 4 shows another embodiment, and an annular taper-shaped portion 80c gradually increasing in diameter toward the fitting cylindrical portion 71 is formed on the outer peripheral side portion of the jig working portion 80a in the seal-up member 8. The tapered portion 80c serves as a support portion that receives and supports the other end portion 71b of the fitting cylindrical portion 71 by its inclined surface (taper surface). The receiving portion (annular tapered portion) 80c is formed concentrically with the fitting cylindrical portion 71, and the lower end portion 71b of the fitting cylindrical portion 71 in each upper seal ring 5 in the stacked state is the receiving portion 80c. It is supported so that it may bite in on the taper surface.

その為、積重なったシールリング５の重量が加わることにより、下端部７１ｂと受支部８０ｃとが互いに楔合するような嵌合関係の受支状態となり、各シールリング５の同心的な積重ね状態が安定し、相互の横ずれの阻止がより確実になされる。従って、前記と同様に、下部のシールリング５における前記アキシャルリップ８１，８２及びラジアルリップ８３に塗布されたグリースＧ１，Ｇ２，Ｇ３が、隣接する上部のシールリング５の下面部に付着することがなく、グリースＧ１，Ｇ２，Ｇ３の所期の塗布量が維持された状態でハブベアリング１に対する組付けがなされ、意図したグリースＧ１，Ｇ２，Ｇ３の前記性能が充分に発揮される。   Therefore, when the weight of the stacked seal rings 5 is added, the fitting state is such that the lower end 71b and the receiving portion 80c are wedged with each other, and the concentric stacked states of the seal rings 5 Are stabilized, and mutual lateral displacement is more reliably prevented. Accordingly, the grease G1, G2, G3 applied to the axial lips 81, 82 and the radial lip 83 in the lower seal ring 5 may adhere to the lower surface portion of the adjacent upper seal ring 5 in the same manner as described above. The assembly of the grease G1, G2, G3 is maintained in the state where the intended application amount of the grease G1, G2, G3 is maintained, and the performance of the intended grease G1, G2, G3 is sufficiently exhibited.

この例の場合、作用部８０ａの外周側部分が環状テーパー形状部８０ｃとされるから、作用部８０ａにおける治具の作用部位が狭められることになる。しかし、嵌合円筒部７１の前記薄肉部分７１ｃは、嵌合円筒部７１の筒壁の内径が、途中から段差状に径大化した状態で形成されているから、その先端の前記他端部７１ｂの当り代としての前記環状テーパー形状部８０ｃは、作用部８０ａの外周側部分の狭い領域に確保すれば充分である。従って、前記作用部位の実質的な狭まりは、前記圧入嵌合の作業性に影響を及ぼす程のものになるものではない。
その他の構成は、前記実施形態と同様であるから、共通部分に同一の符号を付しその説明を割愛する。 In the case of this example, since the outer peripheral side portion of the action portion 80a is an annular tapered portion 80c, the action portion of the jig in the action portion 80a is narrowed. However, the thin-walled portion 71c of the fitting cylindrical portion 71 is formed in a state where the inner diameter of the cylindrical wall of the fitting cylindrical portion 71 is increased in a stepped shape from the middle, so that the other end portion at the tip thereof It is sufficient to secure the annular tapered portion 80c as a contact allowance of 71b in a narrow region on the outer peripheral side portion of the action portion 80a. Therefore, the substantial narrowing of the action part does not affect the workability of the press fitting.
Since other configurations are the same as those of the above-described embodiment, the same reference numerals are given to common portions, and descriptions thereof are omitted.

図５は、更に他の実施形態を示し、前記シールリップ部材８における治具の作用部８０ａの外周側部分に、前記嵌合円筒部７１の他端部７１ｂを嵌受する環状凹溝部８０ｄが形成され、この環状凹溝部８０ｄが前記嵌合円筒部７１の他端部７１ｂを受支する受支部とされている。該受支部（環状凹溝部）８０ｄは、嵌合円筒部７１と同心的に形成されており、積重ね状態の各上部のシールリング５における嵌合円筒部７１の下端部７１ｂは、受支部８０ｄにおける凹部で受支される。その為、各シールリング５の同心的な積重ね状態が安定し、相互の横ずれの阻止がより確実になされる。従って、前記と同様に、下部のシールリング５における前記アキシャルリップ８１，８２及びラジアルリップ８３に塗布されたグリースＧ１，Ｇ２，Ｇ３が、隣接する上部のシールリング５の下面部に付着することがなく、グリースＧ１，Ｇ２，Ｇ３の所期の塗布量が維持された状態でハブベアリング１に対する組付けがなされ、意図したグリースＧ１，Ｇ２，Ｇ３の前記性能が充分に発揮される。   FIG. 5 shows still another embodiment, and an annular groove portion 80d for receiving the other end portion 71b of the fitting cylindrical portion 71 is provided on an outer peripheral side portion of the jig working portion 80a in the seal lip member 8. The annular groove 80d is formed as a receiving portion that receives and supports the other end portion 71b of the fitting cylindrical portion 71. The receiving portion (annular groove portion) 80d is formed concentrically with the fitting cylindrical portion 71, and the lower end portion 71b of the fitting cylindrical portion 71 in each upper seal ring 5 in the stacked state is in the receiving portion 80d. It is supported by the recess. Therefore, the concentric stacked state of each seal ring 5 is stabilized, and the mutual lateral displacement can be more reliably prevented. Accordingly, the grease G1, G2, G3 applied to the axial lips 81, 82 and the radial lip 83 in the lower seal ring 5 may adhere to the lower surface portion of the adjacent upper seal ring 5 in the same manner as described above. The assembly of the grease G1, G2, G3 is maintained in the state where the intended application amount of the grease G1, G2, G3 is maintained, and the performance of the intended grease G1, G2, G3 is sufficiently exhibited.

この例の場合も、作用部８０ａの外周側部分に環状凹溝部８０ｄが形成されることにより、作用部８０ａにおける治具の作用部位が狭められることになるが、前記と同様の薄肉部分７１ｃの形成態様により、環状凹溝部８０ｄが外周側部分の限られた部位に形成されることになる。従って、前記作用部位の実質的な狭まりは、前記圧入嵌合の作業性に影響を及ぼす程のものにならないことは、前記と同様である。
その他の構成は、前記実施形態と同様であるから、ここでも共通部分に同一の符号を付しその説明を割愛する。 Also in this example, the annular concave groove 80d is formed on the outer peripheral portion of the action portion 80a, so that the action portion of the jig in the action portion 80a is narrowed. Depending on the formation mode, the annular groove portion 80d is formed in a limited portion of the outer peripheral side portion. Therefore, as described above, the substantial narrowing of the working part does not become so large as to affect the workability of the press-fitting.
Since other configurations are the same as those of the above-described embodiment, the same reference numerals are given to the common portions and the description thereof is omitted.

尚、前記実施形態では、シールリップ部材８が、ゴムの加硫成型体である例について述べたが、弾性合成樹脂の成型体であっても良い。また、本発明の軸受密封装置が適用される軸受が、ハブベアリングである例について述べたが、これに限定されず、同様に構成されたその他の軸受にも適用することができる。さらに、シールリップ部材８の形状（シールリップの数も含む）、芯金７の形状等も例示のものに限定されるものではない。特に、前記他端部７１ｂの先細状の断面形状は、図例のような略二等辺三角形の所謂両刃形状に限らず、外周側に寄った所謂片刃形状であっても良い。また、芯金７の嵌合円筒部７１が外輪２の内周部２ａに圧入嵌合されるものとしたが、外輪２の外周部に外嵌一体とされるものであっても良い。   In the above-described embodiment, the example in which the seal lip member 8 is a rubber vulcanized molded body has been described, but an elastic synthetic resin molded body may be used. Moreover, although the bearing to which the bearing sealing device of the present invention is applied is a hub bearing, the present invention is not limited to this, and the present invention can be applied to other bearings similarly configured. Furthermore, the shape of the seal lip member 8 (including the number of seal lips), the shape of the cored bar 7 and the like are not limited to those illustrated. In particular, the tapered cross-sectional shape of the other end 71b is not limited to the so-called double-edged shape of a substantially isosceles triangle as shown in the figure, but may be a so-called single-edged shape approaching the outer peripheral side. Further, although the fitting cylindrical portion 71 of the core metal 7 is press-fitted and fitted to the inner peripheral portion 2 a of the outer ring 2, it may be integrally fitted to the outer peripheral portion of the outer ring 2.

１ ハブベアリング（軸受）
２ 外輪
２ａ 外輪の内周部
３Ａ ハブ輪
３ａ ハブフランジ
５ シールリング（軸受密封装置）
７ 芯金
７１ 嵌合円筒部
７１ａ 一端部
７１ｂ 他端部（下端部）
７２ 湾曲形状部
７３ 内向鍔状部
７３ａ 鍔状部の内周縁部
７３ｂ 外面側部
８ シールリップ部材
８０ リップ基部
８０ｂ 受支部（高摩擦係数化処理面）
８０ｃ 受支部（環状テーパー形状部）
８０ｄ 受支部（環状凹溝部）
８１ アキシャルリップ
８２ アキシャルリップ 1 Hub bearing
2 Outer ring 2a Inner peripheral part of outer ring 3A Hub ring 3a Hub flange 5 Seal ring (bearing sealing device)
7 cored bar 71 fitting cylindrical part 71a one end part 71b other end part (lower end part)
72 Curved-shaped portion 73 Inward flange portion 73a Inner peripheral edge portion 73b Outside surface side portion 8 Seal lip member 80 Lip base portion 80b Supporting portion (high friction coefficient treatment surface)
80c Supporting part (annular taper-shaped part)
80d Supporting part (annular groove part)
81 Axial lip 82 Axial lip

Claims (6)

芯金と、該芯金に一体に固着された弾性体からなるシールリップ部材とよりなる軸受密封装置であって、
前記芯金は、軸受外輪に嵌合一体とされる嵌合円筒部と、該嵌合円筒部の一端部より連成され、湾曲形状部分を含んで求心方向に屈曲形成された内向鍔状部とよりなり、
前記シールリップ部材は、前記一端部から前記湾曲形状部分を含む前記鍔状部の内周縁部に亘る外面側部に一体に固着されたリップ基部と、該リップ基部より遠心方向に拡径するよう同心円錐状に形成された複数のアキシャルリップとを備え、
前記リップ基部は、当該軸受密封装置の複数を同心的に積重ねた際、隣接密封装置における前記嵌合円筒部の他端部を受支する受支部を含み、
前記嵌合円筒部の筒壁は、途中から前記他端部に至る部分が薄肉に形成されていることを特徴とする軸受密封装置。 A bearing sealing device comprising a mandrel and a seal lip member made of an elastic body fixed integrally to the mandrel,
The cored bar is formed of a fitting cylindrical portion that is fitted and integrated with the bearing outer ring, and one inward end portion of the fitting cylindrical portion, and an inward saddle-shaped portion that is bent and formed in a centripetal direction including a curved portion. And more
The seal lip member has a lip base integrally fixed to an outer surface side portion extending from the one end to the inner peripheral edge of the bowl-shaped portion including the curved portion, and the diameter of the seal lip member is expanded in the centrifugal direction from the lip base. With a plurality of axial lips formed concentrically conical,
The lip base includes a receiving portion that receives and supports the other end of the fitting cylindrical portion in an adjacent sealing device when a plurality of the bearing sealing devices are concentrically stacked.
The cylindrical wall of the fitting cylindrical part is formed with a thin part from the middle to the other end part. 請求項１に記載の軸受密封装置において、
前記受支部は、粗面化処理による高摩擦係数化処理面とされていることを特徴とする軸受密封装置。 The bearing sealing device according to claim 1,
2. The bearing sealing device according to claim 1, wherein the support portion is a surface with a high friction coefficient treatment by a roughening treatment. 請求項１に記載の軸受密封装置において、
前記受支部が、前記嵌合円筒部の他端部を傾斜面で受支するべく該嵌合円筒部と同心に形成された環状テーパー形状部からなることを特徴とする軸受密封装置。 The bearing sealing device according to claim 1,
2. The bearing sealing device according to claim 1, wherein the receiving portion comprises an annular tapered portion formed concentrically with the fitting cylindrical portion so as to receive the other end portion of the fitting cylindrical portion with an inclined surface. 請求項１に記載の軸受密封装置において、
前記受支部が、前記嵌合円筒部の他端部を嵌受するべく該嵌合円筒部と同心に形成された環状凹溝部からなることを特徴とする軸受密封装置。 The bearing sealing device according to claim 1,
2. The bearing sealing device according to claim 1, wherein the support portion comprises an annular groove portion formed concentrically with the fitting cylindrical portion so as to receive the other end portion of the fitting cylindrical portion. 請求項１乃至４のいずれか１項に記載の軸受密封装置において、
前記嵌合円筒部の他端部の断面形状が先細状とされていることを特徴とする軸受密封装置。 In the bearing sealing device according to any one of claims 1 to 4,
A bearing sealing device, wherein a cross-sectional shape of the other end portion of the fitting cylindrical portion is tapered. 請求項１乃至５のいずれか１項に記載の軸受密封装置において、
前記軸受がハブベアリングであって、前記芯金をしてハブベアリングの外輪内周部に圧入嵌合された状態では、前記アキシャルリップの先側が前記ハブ輪のハブフランジに弾接されるよう構成されていることを特徴とする軸受密封装置。 The bearing sealing device according to any one of claims 1 to 5,
The bearing is a hub bearing, and the front side of the axial lip is elastically brought into contact with the hub flange of the hub wheel when the cored bar is press-fitted into the inner peripheral portion of the outer ring of the hub bearing. A bearing sealing device characterized by being made.
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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103848187A (en) * 2014-03-07 2014-06-11 佛山市加瓦五金制品有限公司 Dust-proof structure for conveying device on kiln
WO2018097233A1 (en) 2016-11-25 2018-05-31 Nok株式会社 Sealing device and hub bearing
JPWO2018096994A1 (en) * 2016-11-25 2019-10-17 Nok株式会社 Sealing device and sealing structure
WO2020009005A1 (en) 2018-07-03 2020-01-09 Nok株式会社 Sealing device
KR20200021592A (en) * 2018-08-21 2020-03-02 (주)진양오일씰 Encoder Sealing Assembly in hub bearings for vehicle
JP2021021435A (en) * 2019-07-26 2021-02-18 光洋シーリングテクノ株式会社 Hub unit sealing device

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103848187A (en) * 2014-03-07 2014-06-11 佛山市加瓦五金制品有限公司 Dust-proof structure for conveying device on kiln
WO2018097233A1 (en) 2016-11-25 2018-05-31 Nok株式会社 Sealing device and hub bearing
JPWO2018096994A1 (en) * 2016-11-25 2019-10-17 Nok株式会社 Sealing device and sealing structure
US10794428B2 (en) 2016-11-25 2020-10-06 Nok Corporation Sealing device and hub bearing
JP7199225B2 (en) 2016-11-25 2023-01-05 Nok株式会社 Sealing device and sealing structure
US11578757B2 (en) 2016-11-25 2023-02-14 Minebea Mitsumi Inc. Sealing apparatus and sealing structure
WO2020009005A1 (en) 2018-07-03 2020-01-09 Nok株式会社 Sealing device
KR20200021592A (en) * 2018-08-21 2020-03-02 (주)진양오일씰 Encoder Sealing Assembly in hub bearings for vehicle
KR102119633B1 (en) * 2018-08-21 2020-06-08 (주)진양오일씰 Encoder Sealing Assembly in hub bearings for vehicle
JP2021021435A (en) * 2019-07-26 2021-02-18 光洋シーリングテクノ株式会社 Hub unit sealing device

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