JP2018071714A - Seal ring and rolling bearing unit with seal ring - Google Patents

Seal ring and rolling bearing unit with seal ring Download PDF

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Publication number
JP2018071714A
JP2018071714A JP2016214043A JP2016214043A JP2018071714A JP 2018071714 A JP2018071714 A JP 2018071714A JP 2016214043 A JP2016214043 A JP 2016214043A JP 2016214043 A JP2016214043 A JP 2016214043A JP 2018071714 A JP2018071714 A JP 2018071714A
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axial direction
ring
seal ring
axial
diameter side
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JP2018071714A5 (en
JP6838354B2 (en
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晴美 高梨
Harumi Takanashi
晴美 高梨
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NSK Ltd
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NSK Ltd
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Priority to JP2016214043A priority Critical patent/JP6838354B2/en
Priority to DE202017106598.7U priority patent/DE202017106598U1/en
Priority to CN201721427509.XU priority patent/CN207634673U/en
Publication of JP2018071714A publication Critical patent/JP2018071714A/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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0073—Hubs characterised by sealing means
    • 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
    • F16C33/723—Shaft end sealing means, e.g. cup-shaped caps or covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a structure of a seal ring which can inexpensively obtain the seal ring capable of securing the sealing performance of an intermediate portion between an axial outer end face of an outer ring and the seal ring.SOLUTION: An outward flange part 20a which is arranged in a state of being bent to the outside of a radial direction from a fixed cylinder part 19a which is internally fixed to an outer end part of an outer ring 2a in an axial direction out of a core grid 17a constituting a seal ring 14a is constituted of a flat plate part 40, a bent part 41 which is curvedly bent to a direction progressing to a single direction in the axial direction as progressing toward the outside of the radial direction, and an inclined plate part 41 which is inclined to a direction progressing to the single direction of the axial direction as progressing toward the outside of the radial direction sequentially from the inside of the radial direction. A salient part 29a which is salient to the inside of the axial direction is formed at an inside diameter side end part of a back face cover part 45 being a part of seal material 18a covering an inside face of the outward flange part 20a in the axial direction. Furthermore, the salient part 29a and a boundary position X of the other side face of the flat plate part 40 in the axial direction and the other side face of the bent part 41 in the axial direction are superimposed on each other in the axial direction.SELECTED DRAWING: Figure 2

Description

本発明は、例えば車両（自動車）の車輪を懸架装置に対して支持する為の車輪支持用転がり軸受ユニットの内部空間を塞ぐ為に使用するシールリングの改良に関する。   The present invention relates to an improvement in a seal ring used to close an internal space of a wheel bearing rolling bearing unit for supporting, for example, a vehicle (automobile) wheel with respect to a suspension device.

例えば図８に示す様に、自動車の車輪は、車輪支持用のシールリング付転がり軸受ユニット１により、懸架装置に対し回転自在に支持されている。このシールリング付転がり軸受ユニット１は、外輪２の内径側にハブ３を、複数個の転動体４、４を介して回転自在に支持している。外輪２は、懸架装置に支持する為の静止側フランジ５を外周面に有しており、複列の外輪軌道６ａ、６ｂを内周面に有している。ハブ３は、ハブ本体７と内輪８とを、ナット９により結合する事により構成されており、外周面に複列の内輪軌道１０ａ、１０ｂを有している。転動体４、４は、内輪軌道１０ａ、１０ｂと外輪軌道６ａ、６ｂとの間に、各列毎に複数個ずつ、それぞれ保持器１１、１１により保持された状態で転動自在に設けられている。   For example, as shown in FIG. 8, a vehicle wheel is rotatably supported by a suspension device by a rolling bearing unit 1 with a seal ring for supporting the wheel. In this rolling bearing unit 1 with a seal ring, a hub 3 is rotatably supported via a plurality of rolling elements 4 and 4 on the inner diameter side of an outer ring 2. The outer ring 2 has a stationary side flange 5 on the outer peripheral surface for supporting the suspension device, and has double-row outer ring raceways 6a and 6b on the inner peripheral surface. The hub 3 is configured by connecting a hub body 7 and an inner ring 8 with a nut 9 and has double-row inner ring raceways 10a and 10b on an outer peripheral surface. The rolling elements 4 and 4 are provided between the inner ring raceways 10a and 10b and the outer ring raceways 6a and 6b so as to be freely rollable while being held by the retainers 11 and 11 for each row. Yes.

ハブ本体７の外周面のうち、外輪２の軸方向外端開口部から軸方向外方に突出した部分には、径方向外方に突出した回転側フランジ１２が設けられている。回転側フランジ１２には、複数本のスタッド１３を利用して、車輪を構成するホイールが取り付けられる。尚、本明細書及び特許請求の範囲で、軸方向に関して内とは、車両への組み付け状態で車両の幅方向中央側となる側を言い、同じく外とは、車両の幅方向外側となる側を言う。   On the outer peripheral surface of the hub body 7, a rotation-side flange 12 protruding radially outward is provided at a portion protruding axially outward from the axial outer end opening of the outer ring 2. A wheel constituting the wheel is attached to the rotation side flange 12 using a plurality of studs 13. In the present specification and claims, “inner” with respect to the axial direction refers to the side that is the central side in the width direction of the vehicle when assembled to the vehicle, and “outside” refers to the side that is the outer side in the width direction of the vehicle. Say.

外輪２の軸方向外端部内周面とハブ３の軸方向中間部外周面との間には、シールリング１４を装着している。これにより、外輪２の内周面とハブ３の外周面との間に存在する内部空間１５の軸方向外端開口部を塞いでいる。一方、外輪２の軸方向内端部には、有底円筒状のカバー１６を装着して、この外輪２の軸方向内端開口部を塞いでいる。   A seal ring 14 is mounted between the inner peripheral surface of the outer end of the outer ring 2 in the axial direction and the outer peripheral surface of the intermediate portion of the hub 3 in the axial direction. As a result, the axially outer end opening of the internal space 15 existing between the inner peripheral surface of the outer ring 2 and the outer peripheral surface of the hub 3 is closed. On the other hand, a bottomed cylindrical cover 16 is attached to the inner end of the outer ring 2 in the axial direction to close the opening of the inner end of the outer ring 2 in the axial direction.

内部空間１５の軸方向外端開口部を塞ぐシールリング１４は、回転側フランジ１２の軸方向内側面に沿って径方向内方に導かれた異物が内部空間１５に侵入するのを防止する必要上、優れたシール性能が要求されている。この様な事情に鑑みて従来から、内部空間の軸方向外端開口部をシールする為のシールリングとして、各種構造のものが考えられている。図９は、特許文献１に記載されたシールリング１４を示している。   The seal ring 14 that closes the axially outer end opening of the internal space 15 needs to prevent foreign matter guided radially inward along the axially inner side surface of the rotation side flange 12 from entering the internal space 15. In addition, excellent sealing performance is required. In view of such circumstances, conventionally, various types of seal rings have been considered as seal rings for sealing the axially outer end opening of the internal space. FIG. 9 shows the seal ring 14 described in Patent Document 1.

シールリング１４は、芯金１７と、シール材１８とから構成されている。このうちの芯金１７は、外輪２の軸方向外端部内周面に内嵌固定された固定筒部１９と、固定筒部１９の軸方向外端部から径方向外方に向けて直角に折れ曲がった外向鍔部２０と、固定筒部１９の軸方向内端部から軸方向外側に向けて１８０度折り返されると共に径方向内方に向けて折れ曲がった内径支持部２１とを備える。又、外向鍔部２０の径方向中間部乃至外端部の軸方向内側に除肉部２２を設ける事で、この外向鍔部２０の径方向中間部乃至外端部を薄板部２３としている。尚、図９を含め各図には、自由状態でのシールリップの形状を示している。   The seal ring 14 includes a cored bar 17 and a sealing material 18. Of these, the metal core 17 includes a fixed cylinder portion 19 that is fitted and fixed to the inner peripheral surface of the outer end 2 in the axial direction, and a right angle from the outer end portion in the axial direction of the fixed cylinder portion 19 outward in the radial direction. The outer flange portion 20 is bent, and the inner diameter support portion 21 is bent 180 degrees outward in the axial direction from the inner end portion in the axial direction of the fixed cylinder portion 19 and bent inward in the radial direction. Further, by providing a thinning portion 22 in the axially inner side of the outward flange portion 20 or the outer end portion in the axial direction, the radial intermediate portion or outer end portion of the outward flange portion 20 is used as a thin plate portion 23. Each figure including FIG. 9 shows the shape of the seal lip in a free state.

シール材１８は、弾性材製で、芯金１７に対し加硫接着により結合固定されており、３本のシールリップ２４〜２６と、外向鍔部２０の周囲を覆う様に設けられた外径側覆部２７と、この外径側覆部２７の外周面から径方向外方に延出した突出部２８とを備えている。   The sealing material 18 is made of an elastic material, and is bonded and fixed to the core metal 17 by vulcanization adhesion. The outer diameter is provided so as to cover the three sealing lips 24 to 26 and the outward flange portion 20. A side cover 27 and a protrusion 28 extending radially outward from the outer peripheral surface of the outer diameter side cover 27 are provided.

３本のシールリップ２４〜２６のうち、軸方向外方に延出する状態で設けられた、サイドリップと呼ばれる軸方向シールリップ２４、２５は、それぞの先端縁を回転側フランジ１２の基端部の軸方向内側面に全周に亙り摺接させている。又、径方向内方に突出する状態で設けられた径方向シールリップ２６は、その先端縁をハブ本体７の軸方向中間部外周面に全周に亙り摺接させている。これにより、内部空間１５の軸方向外端開口部を塞ぎ、泥水等の異物が内部空間１５に侵入するのを防止している。又、外径側覆部２７の径方向中間部から軸方向内方に向けて突出する状態で設けられた突起部２９を、外輪２の軸方向外端面に弾性的に接触させている。これにより、シールリング１４と外輪２の軸方向外端面との間部分を密封している。   Of the three seal lips 24 to 26, the axial seal lips 24, 25 called side lips provided in a state of extending outward in the axial direction have their respective leading edges at the base of the rotary flange 12. It is slidably contacted with the inner circumferential surface of the end portion over the entire circumference. Further, the radial seal lip 26 provided so as to protrude radially inward is in sliding contact with the outer peripheral surface of the hub body 7 in the axially intermediate portion of the hub body 7 over the entire circumference. Thereby, the axial direction outer end opening of the internal space 15 is closed, and foreign matter such as muddy water is prevented from entering the internal space 15. In addition, a protrusion 29 provided in a state of projecting inward in the axial direction from the radial intermediate portion of the outer diameter side covering portion 27 is brought into elastic contact with the axially outer end surface of the outer ring 2. Thereby, a portion between the seal ring 14 and the outer end surface in the axial direction of the outer ring 2 is sealed.

特開２０１３−１９０１０１号公報JP 2013-190101 A

ところで、上述した様なシールリングを構成する芯金は、一般的に、金属板（鋼板）にプレス加工を施す事により造られているが、前記図９に示した構造の様に、外向鍔部２０の軸方向内側に除肉部２２が設けられた芯金１７を造るには、コイニング加工（圧印加工）を施す必要がある。コイニング加工は、通常の曲げ加工を施す場合に比べて、大きなプレス荷重が必要になり、大型のプレス機が必要になる為、製造コストが嵩む原因となる。   Incidentally, the metal core constituting the seal ring as described above is generally manufactured by pressing a metal plate (steel plate). However, as in the structure shown in FIG. In order to manufacture the cored bar 17 provided with the thinned portion 22 on the inner side in the axial direction of the portion 20, it is necessary to perform coining processing (coining processing). The coining process requires a large press load and a large press as compared with the case of performing a normal bending process, which causes an increase in manufacturing cost.

又、一般的なシールリングの製造方法としては、下型内に接着剤を塗布した芯金を配置すると共に、この芯金上にリング状の未加硫ゴムを載置した状態で、下型に対して上型を締め、加硫接着成形する事が行われている。但し、この様な方法により前記図９に示した様なシールリング１４を造る場合には、溶融したゴムが、外向鍔部２０の径方向外側から除肉部２２内に流動する（廻る）際に、この除肉部２２内の空気が抜けずに残留し、溶融したゴムに気泡が形成されてしまい、突起部２９が設計通りに成形されない可能性がある。   As a general method for manufacturing a seal ring, a core metal coated with an adhesive is placed in the lower mold, and a ring-shaped unvulcanized rubber is placed on the metal core. On the other hand, the upper mold is tightened and vulcanized and adhesive molding is performed. However, when the seal ring 14 as shown in FIG. 9 is manufactured by such a method, the molten rubber flows (turns) from the radially outer side of the outward flange 20 into the thinning portion 22. In addition, there is a possibility that air in the thinned portion 22 remains without being removed, bubbles are formed in the melted rubber, and the protruding portion 29 is not molded as designed.

この様な事情に鑑みて、下型の一部に、除肉部２２内のエア抜きを行う為の大気と連通した空間を設け、この空間に意図的に溶融ゴムを流して、余分な溶融ゴムと共に残留空気を下型の成形空間の外へ押し出す事が考えられる。具体的には、図１０に示す様に、除肉部２２の内径側端部近傍にフラッシュランド５４を設け、その中にフラッシュ３０を形成する。ところが、この場合には、フラッシュ３０を切除した際に生じるフラッシュ３０の一部が、外径側覆部２７に残留し易くなる。そして、フラッシュ３０の残留部（バリ部）の先端縁が、突起部２９の先端縁よりも軸方向に突出してしまうと、この突起部２９による密封効果が損なわれてしまう。この様な問題の発生を防止する為に、突起部２９の突出量を大きくする事が考えられるが、この場合には、外輪２の軸方向外端面との接触によって弾性変形した（潰れた）突起部２９を収容する空間を、この突起部２９の径方向両側に設ける必要があり、除肉部２２の径方向寸法を大きく確保しなければならなくなる。そして、この様に除肉部２２の形成範囲を大きくする事は、プレス荷重の増大に繋がる為、製造コストが更に嵩む原因となる。   In view of such circumstances, a part of the lower mold is provided with a space that communicates with the atmosphere for venting the air inside the decarburized portion 22, and molten rubber is intentionally allowed to flow through this space to cause excess melting. It can be considered that residual air is pushed out of the molding space of the lower mold together with the rubber. Specifically, as shown in FIG. 10, a flash land 54 is provided in the vicinity of the inner diameter side end portion of the thinned portion 22, and the flash 30 is formed therein. However, in this case, a part of the flash 30 generated when the flash 30 is cut out easily remains in the outer diameter side cover portion 27. If the tip edge of the remaining portion (burr portion) of the flash 30 protrudes in the axial direction from the tip edge of the protrusion 29, the sealing effect by the protrusion 29 is impaired. In order to prevent the occurrence of such a problem, it is conceivable to increase the protrusion amount of the protrusion 29. In this case, the protrusion 29 is elastically deformed (collapsed) by contact with the outer end surface in the axial direction of the outer ring 2. It is necessary to provide a space for accommodating the protruding portion 29 on both sides in the radial direction of the protruding portion 29, and it is necessary to ensure a large radial dimension of the thinned portion 22. And increasing the formation range of the thinned portion 22 in this way leads to an increase in the press load, which causes a higher manufacturing cost.

本発明は、上述の様な事情に鑑みて、外輪に相当する使用時にも回転しない外径側軌道輪部材の軸方向端面との間部分の密封性を確保できるシールリングを、低コストで得られる構造を実現すべく発明したものである。   In view of the circumstances as described above, the present invention provides a low-cost seal ring that can ensure the sealability between the axial end surface of the outer diameter side race ring member that does not rotate during use corresponding to the outer ring. Invented to realize the structure to be realized.

本発明のシールリング及びシールリング付転がり軸受ユニットのうち、シールリングは、使用時に回転する内径側軌道輪部材の外周面と使用時にも回転しない外径側軌道輪部材の内周面との間に存在する内部空間の軸方向片端開口部を塞ぐ為に使用されるもので、芯金と、この芯金に支持固定された弾性材製のシール材とを備える。
このうちの芯金は、金属板製で全体が円環状に構成されており、前記外径側軌道輪部材の軸方向片端部に固定される固定筒部と、この固定筒部の軸方向片端部から径方向外方に向けて折れ曲がった外向鍔部とを有している。
更にこの外向鍔部は、内径寄り部分に設けられ、前記芯金の中心軸に対し直交する方向に延出した平板部と、この平板部の径方向外側に隣接して設けられ、径方向外方に向かう程軸方向片方に向かう方向に曲線的に屈曲した屈曲部と、この屈曲部の径方向外側に隣接して設けられ、径方向外方に向かう程軸方向片方に向かう方向に直線的に傾斜した傾斜板部とを有している。
前記シール材は、前記外向鍔部の周囲を覆った外径側覆部と、この外径側覆部のうち前記外向鍔部の軸方向他側を覆った背面覆部から軸方向他方に突出する状態で設けられ、前記外径側軌道輪部材の軸方向片端面と全周に亙り接触する突起部と、先端縁を前記内径側軌道輪部材の表面に全周に亙り摺接させる１乃至複数本のシールリップとを有する。
そして、前記平板部の軸方向他側面（直線部）と前記屈曲部の軸方向他側面（曲線部）との境界位置を、前記突起部又は前記背面覆部のうちこの突起部よりも内径側に存在する部分と軸方向に重畳させている。 Among the seal ring and the rolling bearing unit with seal ring of the present invention, the seal ring is between the outer peripheral surface of the inner diameter side bearing ring member that rotates during use and the inner peripheral surface of the outer diameter side bearing ring member that does not rotate during use. Is used for closing the axial one-end opening of the internal space, and includes a cored bar and an elastic sealing material supported and fixed to the cored bar.
Of these, the metal core is made of a metal plate and is formed in an annular shape as a whole, a fixed cylinder part fixed to one end part in the axial direction of the outer diameter side race ring member, and one axial end part of the fixed cylinder part And an outward flange that is bent radially outward from the portion.
Further, the outward flange portion is provided near the inner diameter, and is provided adjacent to a flat plate portion extending in a direction orthogonal to the central axis of the cored bar and radially outward of the flat plate portion. A bent portion that is curved in a direction toward one side in the axial direction as it goes toward the outer side, and is provided adjacent to a radially outer side of the bent portion, and is linear in a direction toward one side in the axial direction toward the outer side in the radial direction. And an inclined plate portion that is inclined.
The sealing material protrudes in the other axial direction from an outer diameter side cover that covers the periphery of the outward flange, and a back cover that covers the other side of the outer flange in the axial direction of the outer diameter side cover. And a projecting portion that is in contact with one end surface in the axial direction of the outer diameter side race ring member over the entire circumference, and a tip edge that is in sliding contact with the surface of the inner diameter side race ring member over the entire circumference. And a plurality of seal lips.
The boundary position between the other axial side surface (straight portion) of the flat plate portion and the other axial side surface (curved portion) of the bent portion is set to the inner diameter side of the protruding portion or the rear cover portion than the protruding portion. Is overlapped in the axial direction with the existing portion.

上述した様な本発明のシールリングを実施する場合には、例えば、前記背面覆部の内径側端部に前記突起部を設け、前記境界位置を、この突起部と軸方向に重畳させる事ができる。   When the seal ring of the present invention as described above is implemented, for example, the protrusion may be provided on the inner diameter side end of the back cover, and the boundary position may be overlapped with the protrusion in the axial direction. it can.

或いは、前記境界位置を、前記背面覆部のうち前記突起部よりも内径側に存在する背面内径部と軸方向に重畳させる事ができる。
又、前記背面内径部を、前記突起部に近い外径寄り部分に設けられた厚肉部と、この厚肉部の径方向内側に隣接して設けられ、この厚肉部よりも軸方向厚さ寸法が小さい薄肉部とを有するものとする。
更に、前記薄肉部の軸方向他側面を、前記厚肉部の軸方向他側面よりも軸方向片側に位置（オフセット）させる。
この様なシールリングを製造するには、例えば、前記芯金に前記シール材を加硫接着する際に、前記薄肉部の軸方向他側面に連続する状態で設けられたフラッシュランド内に、フラッシュを形成する。その後、このフラッシュを切除する。これにより、このフラッシュの一部（残留部）が前記薄肉部に残存した場合にも、このフラッシュの残留部が、前記厚肉部の軸方向他側面よりも軸方向他側に突出しない様にする。 Alternatively, the boundary position can be overlapped in the axial direction with a rear inner diameter portion that exists on the inner diameter side with respect to the protruding portion of the rear cover portion.
Further, the inner diameter portion of the back surface is provided adjacent to the thick-walled portion provided near the outer diameter near the protrusion and the radially inner side of the thick-walled portion. It shall have a thin part with a small dimension.
Further, the other axial side surface of the thin portion is positioned (offset) on one axial side than the other axial side surface of the thick portion.
In order to manufacture such a seal ring, for example, when the sealing material is vulcanized and bonded to the core metal, a flash land is provided in a flash land provided in a state continuous with the other axial side surface of the thin portion. Form. The flash is then excised. As a result, even when a part of the flash (residual part) remains in the thin part, the residual part of the flash does not protrude beyond the other axial side surface of the thick part. To do.

本発明のシールリング付転がり軸受ユニットは、外輪と、ハブと、複数個の転動体と、シールリングとを備える。
このうちの外輪は、前記外径側軌道輪部材に相当し、使用時にも回転しないもので、例えば略円筒状に構成され、内周面に外輪軌道が設けられている。
前記ハブは、前記内径側軌道輪部材に相当し、使用時に回転するもので、前記外輪の内径側にこの外輪と同心に配置されており、外周面のうちで、前記外輪軌道と対向する部分に内輪軌道が設けられている。
前記各転動体は、前記外輪軌道と前記内輪軌道との間に、例えば保持器により保持された状態で、転動自在に設けられている。
前記シールリングは、前記外輪の内周面と前記ハブの外周面との間に存在する内部空間の軸方向外端開口部を塞ぐものであり、芯金と、この芯金に支持されたゴムの如きエラストマー等の弾性材製のシール材とを有している。
そして、前記シールリングとして、本発明のシールリングを使用する。 The rolling bearing unit with a seal ring of the present invention includes an outer ring, a hub, a plurality of rolling elements, and a seal ring.
Among these, the outer ring corresponds to the outer diameter side raceway member and does not rotate during use. For example, the outer race is configured in a substantially cylindrical shape, and an outer raceway is provided on the inner peripheral surface.
The hub corresponds to the inner diameter side raceway member, and rotates when in use. The hub is disposed concentrically with the outer race on the inner diameter side of the outer ring, and a portion of the outer peripheral surface facing the outer ring raceway. Is provided with an inner ring raceway.
Each of the rolling elements is provided between the outer ring raceway and the inner ring raceway so as to be able to roll while being held by a cage, for example.
The seal ring closes an axially outer end opening of an internal space existing between the inner peripheral surface of the outer ring and the outer peripheral surface of the hub, and a metal core and a rubber supported by the metal core And a sealing material made of an elastic material such as an elastomer.
The seal ring of the present invention is used as the seal ring.

上述の様な構成を有する本発明によれば、外径側軌道輪部材の軸方向片端面との間部分の密封性を確保できるシールリングを低コストで得られる。
即ち、本発明の場合には、シールリングを構成する芯金の外向鍔部の外径寄り部分に、径方向外方に向かう程軸方向片方に向かう方向に傾斜した傾斜板部を設けている為、従来構造の様に薄肉部を設けた場合と同様に、外向鍔部の軸方向他側に、外径側軌道輪部材の軸方向片端面との間部分を密封する為の背面覆部の成形空間を設ける事ができる。しかも、傾斜板部は、コイニング加工ではなく、通常の曲げ加工により形成できる為、大型のプレス装置を用いずに、小型のプレス装置により加工する事が可能になる。従って、本発明によれば、外径側軌道輪部材の軸方向片端面との間部分の密封性を確保できるシールリングを、低コストで得られる。 According to the present invention having the above-described configuration, it is possible to obtain a seal ring that can ensure the sealing performance between the outer diameter side race ring member and the one axial end surface thereof at a low cost.
In other words, in the case of the present invention, an inclined plate portion that is inclined in a direction toward one axial direction as it goes outward in the radial direction is provided at a portion near the outer diameter of the outward flange portion of the core metal constituting the seal ring. Therefore, as in the case of providing a thin wall portion as in the conventional structure, a back cover portion for sealing a portion between the axial end of the outer diameter side race ring member on the other axial side of the outward flange portion Forming space can be provided. In addition, since the inclined plate portion can be formed not by coining but by ordinary bending, it can be processed by a small press without using a large press. Therefore, according to this invention, the seal ring which can ensure the sealing performance of the part between the axial direction one end surfaces of the outer diameter side bearing ring member can be obtained at low cost.

本発明の実施の形態の第１例を示す、シールリング付転がり軸受ユニットを示す断面図。Sectional drawing which shows the rolling bearing unit with a seal ring which shows the 1st example of embodiment of this invention. 同じく図１のＡ部拡大図。The A section enlarged view of FIG. 1 similarly. 同じく図２の上部拡大図。The upper enlarged view of FIG. 2 similarly. 同じく金型装置を利用してシール材を加硫接着する状態を説明する為に示す、図３のＢ部に相当する部分の断面模式図。The cross-sectional schematic diagram of the part corresponded to the B section of FIG. 3 shown in order to illustrate the state which vulcanizes-bonds a sealing material similarly using a metal mold apparatus. 本発明の実施の形態の第２例を示す、図２に相当する図。The figure equivalent to FIG. 2 which shows the 2nd example of embodiment of this invention. 同じく図３に相当する図。The figure which corresponds to FIG. 3 similarly. 同じく図６のＣ部拡大図。The C section enlarged view of FIG. 6 similarly. 従来構造のシールリング付転がり軸受ユニットを示す断面図。Sectional drawing which shows the rolling bearing unit with a seal ring of a conventional structure. 図８のＤ部に相当する拡大図。The enlarged view equivalent to the D section of FIG. シールリングを製造する際に形成するフラッシュを説明する為に示す断面図。Sectional drawing shown in order to demonstrate the flash | flush formed when manufacturing a seal ring.

［実施の形態の第１例］
本発明の実施の形態の第１例に就いて、図１〜４を参照しつつ説明する。本例のシールリング付転がり軸受ユニット１ａは、自動車の車輪（従動輪）を懸架装置に対して回転自在に支持する為のもので、外輪２ａと、ハブ３ａと、複数個の転動体（玉）４ａ、４ａと、シールリング１４ａと、カバー１６ａとを備えている。 [First example of embodiment]
A first example of the embodiment of the present invention will be described with reference to FIGS. A rolling bearing unit 1a with a seal ring of this example is for rotatably supporting a wheel (driven wheel) of an automobile with respect to a suspension device, and includes an outer ring 2a, a hub 3a, and a plurality of rolling elements (balls). 4a, 4a, a seal ring 14a, and a cover 16a.

外輪２ａは、例えば中炭素鋼等の鉄系合金製で略円筒状に構成されており、内周面に複列の外輪軌道６ｃ、６ｄを、外周面に静止側フランジ５ａを、それぞれ有している。この様な外輪２ａは、使用時に、静止側フランジ５ａを、図示しない懸架装置のナックルに結合固定する事により、この懸架装置に支持された状態で回転しない。   The outer ring 2a is made of an iron-based alloy such as medium carbon steel and has a substantially cylindrical shape. The outer ring 2a has double-row outer ring raceways 6c and 6d on the inner peripheral surface, and a stationary flange 5a on the outer peripheral surface. ing. In use, the outer ring 2a does not rotate while being supported by the suspension device by fixing the stationary flange 5a to a knuckle of the suspension device (not shown).

ハブ３ａは、ハブ本体７ａと内輪８ａとを結合する事により構成されており、外輪２ａの内径側にこの外輪２ａと同心に配置されている。ハブ本体７ａは、例えば中炭素鋼等の鉄系合金製で、外周面に例えば高周波焼き入れ処理などの硬化熱処理が施されている。   The hub 3a is configured by connecting a hub body 7a and an inner ring 8a, and is disposed concentrically with the outer ring 2a on the inner diameter side of the outer ring 2a. The hub body 7a is made of, for example, an iron-based alloy such as medium carbon steel, and has an outer peripheral surface subjected to hardening heat treatment such as induction hardening.

ハブ本体７ａの外周面のうち、外輪２ａの軸方向外端開口から軸方向外方に突出した部分には、車輪やディスクロータを支持固定する為の円輪状の回転側フランジ１２ａが設けられている。回転側フランジ１２ａのうち、径方向内端部（基端部）を、軸方向に関する厚さ寸法（肉厚）が大きい基半部３１としており、径方向中間部乃至外端部（先端部）を、軸方向に関する厚さ寸法が基半部３１に比べて小さい先半部３２としている。これにより、旋回走行等に伴って、車輪から回転側フランジ１２ａに加わるモーメント（旋回モーメント）に対する強度及び剛性を確保している。又、基半部３１と先半部３２とを、回転側フランジ１２ａの軸方向内側面の内径寄り部分に設けられた段部３３により連続させている。   A portion of the outer peripheral surface of the hub body 7a that protrudes outward in the axial direction from the axial outer end opening of the outer ring 2a is provided with an annular rotation-side flange 12a for supporting and fixing the wheel and the disk rotor. Yes. Of the rotation-side flange 12a, the radially inner end portion (base end portion) is a base half portion 31 having a large thickness dimension (thickness) in the axial direction, and the radially intermediate portion or outer end portion (tip end portion). The tip half 32 is smaller in thickness than the base half 31 in the axial direction. Thereby, the strength and rigidity with respect to the moment (turning moment) applied from the wheel to the rotation-side flange 12a in accordance with turning traveling or the like is ensured. Further, the base half portion 31 and the tip half portion 32 are made continuous by a step portion 33 provided on a portion closer to the inner diameter of the inner side surface in the axial direction of the rotation side flange 12a.

又、ハブ本体７ａの外周面のうち、外輪２ａの内周面に設けられた外側列の外輪軌道６ｃと対向する部分には、断面形状が部分円弧状である内輪軌道１０ｃを設けている。又、ハブ本体７ａの外周面のうち、内輪軌道１０ｃの軸方向外側に隣接した部分には、外径寸法が軸方向に亙り変化しない円筒面部３４を設けている。又、この円筒面部３４と、回転側フランジ１２ａ（基半部３１）の軸方向内側面との間には、断面形状が部分円弧形の凹曲面部３５を設けている。更に、ハブ本体７ａの外周面の軸方向内端部には、小径段部３６を設けている。   In addition, an inner ring raceway 10c having a partial arc shape in cross section is provided at a portion of the outer peripheral face of the hub body 7a facing the outer ring raceway 6c in the outer row provided on the inner peripheral face of the outer ring 2a. A cylindrical surface portion 34 whose outer diameter dimension does not change in the axial direction is provided on a portion of the outer peripheral surface of the hub body 7a adjacent to the outer side in the axial direction of the inner ring raceway 10c. A concave curved surface portion 35 having a partial arc shape in cross section is provided between the cylindrical surface portion 34 and the inner side surface in the axial direction of the rotation side flange 12a (base half portion 31). Further, a small-diameter step portion 36 is provided at the inner end portion in the axial direction of the outer peripheral surface of the hub body 7a.

ハブ本体７ａと共にハブ３ａを構成する内輪８ａは、例えばＳＵＪ２等の高炭素クロム軸受鋼製で略円環状に構成されており、ズブ焼き入れ等の熱処理が施されている。又、内輪８ａの外周面には、断面形状が部分円弧形である内側列の内輪軌道１０ｄが形成されている。この様な内輪８ａは、ハブ本体７ａの軸方向内端部に設けられた小径段部３６に、締り嵌めにより外嵌固定されている。そして、内輪８ａは、ハブ本体７ａの軸方向内端部を径方向外方に塑性変形する事により形成されたかしめ部３７により、軸方向内端面が抑え付けられている。尚、ハブ本体７ａの軸方向内端部にかしめ部３７を形成する構造に代えて、ハブ本体の軸方向内端部にナットを螺着する構造を採用する事もできる。   The inner ring 8a that constitutes the hub 3a together with the hub body 7a is made of a high carbon chrome bearing steel such as SUJ2 and has a substantially annular shape, and is subjected to heat treatment such as quenching. Further, an inner ring raceway 10d in an inner row having a partial arc shape in cross section is formed on the outer peripheral surface of the inner ring 8a. Such an inner ring 8a is externally fixed to the small-diameter step portion 36 provided at the inner end in the axial direction of the hub body 7a by an interference fit. The inner ring 8a has its axial inner end face held down by a caulking portion 37 formed by plastic deformation of the axial inner end of the hub body 7a radially outward. Instead of the structure in which the caulking portion 37 is formed at the inner end portion in the axial direction of the hub body 7a, a structure in which a nut is screwed onto the inner end portion in the axial direction of the hub body can be employed.

転動体４ａ、４ａは、外側列の外輪軌道６ｃ及び内輪軌道１０ｃとの間部分、並びに、内側列の外輪軌道６ｄ及び内輪軌道１０ｄとの間部分に、それぞれ保持器１１ａ、１１ａにより保持された状態で転動自在に配置されている。又、転動体４ａ、４ａには、かしめ部３７による押し付け力を利用して、背面組合せ型の接触角と適正な予圧が付与されている。尚、図示の例では、転動体４ａ、４ａとして玉を使用しているが、重量が嵩む自動車の車輪支持用のシールリング付転がり軸受ユニットの場合には、玉に代えて円すいころを使用する事もできる。   The rolling elements 4a and 4a are held by retainers 11a and 11a, respectively, between the outer ring raceway 6c and the inner ring raceway 10c in the outer row and between the outer ring raceway 6d and the inner ring raceway 10d in the inner row. It is arranged to roll freely in the state. The rolling elements 4a and 4a are given a contact angle of the rear combination type and an appropriate preload by using the pressing force by the caulking portion 37. In the illustrated example, balls are used as the rolling elements 4a and 4a. However, in the case of a rolling bearing unit with a seal ring for supporting a wheel of an automobile having a heavy weight, a tapered roller is used instead of the ball. You can also do things.

外輪２ａの内周面とハブ３ａの外周面との間に存在する、内部空間（転動体設置空間）１５ａの軸方向両端開口を、シールリング１４ａ及びカバー１６ａにより塞いでいる。このうちのカバー１６ａは、外輪２ａの軸方向内端開口部を塞ぐ事により、内部空間１５ａの軸方向内端開口を塞ぐもので、全体を有底円筒状に構成されており、円筒状の支持筒部３８と、この支持筒部３８の軸方向内端部から径方向内方に折れ曲がった底板部３９とを備えている。そして、このうちの支持筒部３８を、外輪２ａの軸方向内端部に内嵌固定する事で、中実体であるハブ本体７ａの軸方向内側面と共に、内部空間１５ａの軸方向内端開口を塞いでいる。   Both ends in the axial direction of the internal space (rolling element installation space) 15a existing between the inner peripheral surface of the outer ring 2a and the outer peripheral surface of the hub 3a are closed by the seal ring 14a and the cover 16a. Of these, the cover 16a closes the axially inner end opening of the inner space 15a by closing the axially inner end opening of the outer ring 2a. The entire cover 16a has a bottomed cylindrical shape. A support cylinder part 38 and a bottom plate part 39 that is bent radially inward from the axially inner end of the support cylinder part 38 are provided. Of these, the supporting cylinder portion 38 is fitted and fixed to the inner end portion in the axial direction of the outer ring 2a, thereby opening the inner end portion in the axial direction of the inner space 15a together with the inner side surface in the axial direction of the hub body 7a. Is blocking.

シールリング１４ａは、内部空間１５ａの軸方向外端開口を塞ぐもので、芯金１７ａと、シール材１８ａとから構成されている。このうちの芯金１７ａは、鋼板等の金属板に打ち抜き及び曲げ等のプレス加工を施す事により、断面略横Ｔ字形で全体を円環状に構成されており、円筒状の固定筒部１９ａと、固定筒部１９ａの軸方向外端部から径方向外方に向けて折れ曲がった外向鍔部２０ａと、固定筒部１９ａの軸方向内端部から軸方向外側に向けて折り返されると共に径方向内方に向けて折れ曲がった内径支持部２１ａとを備えている。そして、このうちの固定筒部１９ａを、外輪２ａの軸方向外端部内周面に締り嵌めで内嵌固定している。   The seal ring 14a closes the axially outer end opening of the internal space 15a, and includes a cored bar 17a and a sealing material 18a. Of these, the metal core 17a is formed in an annular shape with a substantially horizontal T-shaped cross section by punching and bending a metal plate such as a steel plate, and has a cylindrical fixed cylinder portion 19a. The outward flange portion 20a that is bent radially outward from the axially outer end portion of the fixed cylindrical portion 19a, and the axially inner end portion of the fixed cylindrical portion 19a that is folded outward from the axial direction and radially inward. And an inner diameter support portion 21a bent toward the direction. Of these, the fixed cylinder portion 19a is internally fitted and fixed to the inner peripheral surface of the outer end 2a in the axial direction by an interference fit.

本例の場合、外向鍔部２０ａを、平板部４０と、屈曲部４１と、傾斜板部４２とにより構成しており、その外径寸法を、外輪２ａの軸方向外端部外周面の外径寸法よりも大きくしている。この様な外向鍔部２０ａを構成する平板部４０は、芯金１７ａの中心軸に対し直交する方向に延出する状態で、外向鍔部２０ａの内径側部分に設けられている。又、屈曲部４１は、平板部４０の径方向外側に隣接する状態で、外向鍔部２０ａの径方向中間部に設けられている。又、屈曲部４１は、径方向外方に向かう程軸方向外方に向かう方向に曲線的に屈曲している。又、傾斜板部４２は、屈曲部４１の径方向外側に隣接する状態で、外向鍔部２０ａの外径側部分に設けられている。又、傾斜板部４２は、径方向外方に向かう程軸方向外方に向かう方向に直線的に傾斜しており、平板部４０に対する傾斜角度は、３°〜２０°（好ましくは４°〜５°、図示の例は４．５°）である。本例の場合には、この様な構成を有する芯金１７ａを、大きなプレス荷重が必要になるコイニング加工によらず、小さなプレス荷重での加工が可能である通常の曲げ加工により形成している。   In the case of this example, the outward flange portion 20a is constituted by a flat plate portion 40, a bent portion 41, and an inclined plate portion 42, and the outer diameter of the outward flange portion 20a is outside the outer peripheral surface of the outer peripheral portion in the axial direction of the outer ring 2a. It is larger than the diameter. The flat plate portion 40 constituting such an outward flange portion 20a is provided on the inner diameter side portion of the outward flange portion 20a in a state of extending in a direction orthogonal to the central axis of the cored bar 17a. Further, the bent portion 41 is provided at the radially intermediate portion of the outward flange portion 20a in a state adjacent to the radially outer side of the flat plate portion 40. Further, the bent portion 41 is bent in a curve in a direction toward the outer side in the axial direction as it goes outward in the radial direction. Further, the inclined plate portion 42 is provided on the outer diameter side portion of the outward flange portion 20a in a state adjacent to the radially outer side of the bent portion 41. Further, the inclined plate portion 42 is linearly inclined in the axially outward direction as it goes outward in the radial direction, and the inclination angle with respect to the flat plate portion 40 is 3 ° to 20 ° (preferably 4 ° to 4 °). 5 °, and the example shown is 4.5 °). In the case of this example, the cored bar 17a having such a configuration is formed by a normal bending process that can be processed with a small press load, not a coining process that requires a large press load. .

シール材１８ａは、ゴムの如きエラストマー等の弾性材製で、芯金１７ａの軸方向外側面及び内外両周面を覆う状態で、この芯金１７ａに加硫接着により結合されている。この様なシール材１８ａには、３本の接触式シールリップ２４ａ〜２６ａと、外径側覆部２７ａと、突起部２９ａと、補助リップ４３とを備えている。   The sealing material 18a is made of an elastic material such as an elastomer such as rubber, and is bonded to the core metal 17a by vulcanization adhesion while covering the outer surface in the axial direction and the inner and outer peripheral surfaces of the core metal 17a. Such a sealing material 18 a includes three contact-type seal lips 24 a to 26 a, an outer diameter side covering portion 27 a, a protruding portion 29 a, and an auxiliary lip 43.

３本のシールリップ２４ａ〜２６ａのうち、軸方向外方に延出する状態で設けられた、サイドリップと呼ばれる軸方向シールリップ２４ａ、２５ａは、それぞの先端縁を回転側フランジ１２ａの基端部の軸方向内側面に全周に亙り摺接させている。又、径方向内方に突出する状態で設けられた径方向シールリップ２６ａは、その先端縁をハブ本体７ａの軸方向中間部外周面（円筒面部３４）に全周に亙り摺接させている。これにより、内部空間１５ａの軸方向外端開口部を塞ぎ、泥水等の異物が内部空間１５ａに侵入するのを防止している。   Of the three seal lips 24a to 26a, the axial seal lips 24a and 25a, called side lips, provided in a state of extending outward in the axial direction have their respective leading edges at the base of the rotation side flange 12a. It is slidably contacted with the inner circumferential surface of the end portion over the entire circumference. Further, the radial seal lip 26a provided in a state of projecting radially inward is slidably contacted with the outer peripheral surface (cylindrical surface portion 34) of the hub body 7a in the axial direction on the entire circumference. . Thereby, the axial direction outer end opening of the internal space 15a is closed, and foreign matter such as muddy water is prevented from entering the internal space 15a.

又、図示の例では、軸方向シールリップ２４ａ、２５ａを、それぞれ基端縁から先端縁に向かう程、外部空間（内部空間１５ａと反対側）に向かう方向に傾斜させている。これにより、軸方向シールリップ２４ａ、２５ａによる異物侵入防止機能を高めている。これに対し、径方向シールリップ２６ａを、基端縁である外径側端縁から先端縁である内径側端縁に向かう程、内部空間１５ａの軸方向中央側に向かう方向に傾斜させている。これにより、径方向シールリップ２６ａによるグリース漏洩防止機能を高めている。   In the illustrated example, the axial seal lips 24a and 25a are inclined in the direction toward the external space (the side opposite to the internal space 15a) from the base end edge toward the tip end edge. Thereby, the foreign matter intrusion preventing function by the axial seal lips 24a, 25a is enhanced. On the other hand, the radial seal lip 26a is inclined in the direction toward the axially central side of the internal space 15a as it goes from the outer diameter side edge as the base edge toward the inner diameter side edge as the tip edge. . Thereby, the grease leakage prevention function by the radial seal lip 26a is enhanced.

外径側覆部２７ａは、外向鍔部２０ａの周囲（軸方向両側及び径方向外側）を覆う様に設けられており、シールリング１４ａを外輪２ａに対して取り付けた状態で、この外輪２ａの軸方向外端部外周面よりも径方向外側に突出している。又、外径側覆部２７ａは、外向鍔部２０ａの軸方向外側を覆った表面覆部４４と、外向鍔部２０ａの軸方向内側を覆った背面覆部４５と、外向鍔部２０の径方向外側を覆った外周覆部４６とを有している。又、これら表面覆部４４と背面覆部４５と外周覆部４６とは、それぞれ連続している。   The outer diameter side cover portion 27a is provided so as to cover the periphery of the outward flange portion 20a (both sides in the axial direction and the outer side in the radial direction), and with the seal ring 14a attached to the outer ring 2a, It protrudes radially outward from the outer peripheral surface of the axially outer end portion. The outer diameter side cover portion 27a includes a surface cover portion 44 covering the outer side in the axial direction of the outward flange portion 20a, a back surface cover portion 45 covering the inner side in the axial direction of the outward flange portion 20a, and the diameter of the outward flange portion 20. And an outer peripheral cover portion 46 covering the outer side in the direction. Further, the front surface covering portion 44, the back surface covering portion 45, and the outer peripheral covering portion 46 are respectively continuous.

表面覆部４４の内径側部分は、芯金１７ａを構成する内径支持部２１ａの軸方向外側を覆ったシール材１８ａの一部に連続している。これに対し、背面覆部４５は、外向鍔部２０ａの軸方向内側面の径方向中間部乃至外端部に亙る範囲を覆っており、この外向鍔部２０ａの軸方向内側面の内径側端部は覆っていない。より具体的には、背面覆部４５の内径側端縁部は、直線状の平板部４０の軸方向内側面と曲線状（円弧状）の屈曲部４１の軸方向内側面との境界位置（Ｒ止まり）Ｘよりも、僅かに径方向内側に位置している。又、表面覆部４４の軸方向厚さ寸法は、背面覆部４５の軸方向厚さ寸法よりも大きくなっている。   The inner diameter side portion of the surface covering portion 44 is continuous with a part of the sealing material 18a that covers the outer side in the axial direction of the inner diameter support portion 21a constituting the cored bar 17a. On the other hand, the back cover 45 covers a range extending from the radially intermediate portion to the outer end of the axial inner surface of the outward flange 20a, and the inner diameter side end of the axial inner surface of the outward flange 20a. The part is not covered. More specifically, the inner diameter side edge of the back cover 45 is a boundary position between the axial inner surface of the linear flat plate portion 40 and the axial inner surface of the curved (arc-shaped) bent portion 41 ( R stop) It is located slightly inward in the radial direction from X. Further, the axial thickness dimension of the front surface covering portion 44 is larger than the axial thickness dimension of the back surface covering portion 45.

突起部２９ａは、断面略三角形状（直角三角形状）であり、背面覆部４５の内径側端部から軸方向内方に突出する状態で、全周に亙り設けられている。特に本例の場合には、突起部２９ａを、直線状の平板部４０の軸方向内側面と曲線状の屈曲部４１の軸方向内側面との境界位置（Ｒ止まり）Ｘと軸方向に重畳させている。又、突起部２９ａの先端縁（軸方向内端縁）は、外径側覆部２７ａのうちで最も軸方向内方に位置している。この様な突起部２９ａは、シールリング１４ａを外輪２ａに取り付けた状態で、この外輪２ａの軸方向外端面と接触して、径方向内方に弾性的に変形し（潰れ）、外輪２ａの軸方向外端面と平板部４０の軸方向内側面との間に形成された空間４７内に収容される。又、シールリング１４ａの取付状態では、背面覆部４５のうち、突起部２９ａが設けられた部分よりも径方向外側部分に就いても、外輪２ａの軸方向外端面と弾性的に面接触する。   The protrusion 29a has a substantially triangular cross section (right triangle), and is provided over the entire circumference in a state of protruding inward in the axial direction from the inner diameter side end of the back cover 45. In particular, in the case of this example, the protrusion 29a is superimposed on the boundary position (R stop) X between the axial inner surface of the linear flat plate portion 40 and the axial inner surface of the curved bent portion 41 in the axial direction. I am letting. Further, the leading end edge (the inner end edge in the axial direction) of the projecting portion 29a is located on the innermost side in the axial direction in the outer diameter side covering portion 27a. Such a protruding portion 29a is in a state where the seal ring 14a is attached to the outer ring 2a, contacts the outer end surface in the axial direction of the outer ring 2a, and is elastically deformed (collapsed) radially inwardly. It is accommodated in a space 47 formed between the axially outer end surface and the axially inner side surface of the flat plate portion 40. Further, in the attached state of the seal ring 14a, even in the radially outer portion of the back cover 45 than the portion provided with the protruding portion 29a, the surface contact is elastically brought into contact with the axially outer end surface of the outer ring 2a. .

補助リップ４３は、表面覆部４４の径方向中間部に、軸方向外方に突出する状態で全周に亙り設けられている。又、補助リップ４３は、軸方向外方（先端側）に向かう程、径方向外方に向かう方向に傾斜しており、その先端縁を、回転側フランジ１２ａの段部３３に対し、微小隙間を介して近接対向させている。これにより、補助リップ４３の先端縁と段部３３との間に、ラビリンスシールを形成している。   The auxiliary lip 43 is provided over the entire circumference in a state of projecting outward in the axial direction at a radially intermediate portion of the surface covering portion 44. Further, the auxiliary lip 43 is inclined in the radially outward direction as it goes outward in the axial direction (front end side), and the front end edge thereof has a minute gap with respect to the step portion 33 of the rotation side flange 12a. Is placed in close proximity to each other. Thereby, a labyrinth seal is formed between the tip edge of the auxiliary lip 43 and the step portion 33.

本例の場合には、以下の手順により、シール材１８ａを芯金１７ａに対して加硫接着させる。
先ず、図４に示した様に、所定の形状に曲げ加工した芯金１７ａの表面に、接着剤（図示省略）を塗布した状態で、金型装置（加硫型）を構成する下型４８内にセットする。次いで、芯金１７ａ上（図４の左側）に、リング状の未加硫ゴム（図示省略）を載置した状態で、下型４８に対して上型４９を締め付け（型締めを行い）、内部に熱及び圧力を加える。本例の場合には、この様に型締めを行った状態で、上型４９の内側に間欠的に設けられた複数の抑え部５０を、外向鍔部２０ａの内径側端部（平板部４０）の軸方向外側面に対して押し付ける。この際、外向鍔部２０ａの内径側端部の軸方向内側面を、下型４８に設けられた平坦面状の支承面５１によって支持する。つまり、外向鍔部２０ａの内径側端部を、上型４９の抑え部５０と下型４８の支承面５１との間で強く挟持して、金型に対する芯金１７ａの位置決めを図る。 In the case of this example, the sealing material 18a is vulcanized and bonded to the core metal 17a by the following procedure.
First, as shown in FIG. 4, the lower mold 48 constituting the mold apparatus (vulcanizing mold) is applied with an adhesive (not shown) applied to the surface of the core metal 17a bent into a predetermined shape. Set in. Next, with the ring-shaped unvulcanized rubber (not shown) placed on the metal core 17a (left side in FIG. 4), the upper die 49 is clamped (clamping is performed) against the lower die 48, Apply heat and pressure inside. In the case of this example, in a state where the mold is clamped in this way, the plurality of holding portions 50 provided intermittently inside the upper die 49 are connected to the inner diameter side end portions (flat plate portions 40) of the outward flange portions 20a. ) Against the outer surface in the axial direction. At this time, the inner surface in the axial direction of the inner diameter side end portion of the outward flange portion 20 a is supported by a flat bearing surface 51 provided on the lower die 48. That is, the inner diameter side end portion of the outward flange portion 20a is strongly held between the holding portion 50 of the upper die 49 and the support surface 51 of the lower die 48, thereby positioning the core metal 17a with respect to the die.

溶融したゴムは、外向鍔部２０ａの径方向外側を通過し、この外向鍔部２０の軸方向内側面と下型４８の内面との間に形成された背面覆部成形空間５２に流動する。そして、この背面覆部成形空間５２を、径方向外側から径方向内側に向けて流動する。本例の場合には、下型４８の内面のうち、背面覆部成形空間５２の内径側端部で、且つ、前記境界位置Ｘと対向する部分に、突起部２９ａを形成する為の突起部成形空間５３が形成されていると共に、この突起部成形空間５３の奥端部に連通する状態で、フラッシュランド５４が形成されたものを使用している。この為、背面覆部成形空間５２を径方向内側に向けて流動した溶融ゴムは、突起部成形空間５３に残留した空気を排出しつつ、突起部成形空間５３及びフラッシュランド５４に順次流動する。   The molten rubber passes through the radially outer side of the outward flange 20 a and flows into the back cover molding space 52 formed between the axial inner surface of the outward flange 20 and the inner surface of the lower die 48. The back cover forming space 52 flows from the radially outer side toward the radially inner side. In the case of this example, of the inner surface of the lower mold 48, the protrusion for forming the protrusion 29 a at the inner diameter side end of the back cover forming space 52 and at the portion facing the boundary position X. A molding space 53 is formed, and a flash land 54 is formed in a state where the molding land 53 communicates with the rear end of the projection molding space 53. Therefore, the molten rubber that has flowed toward the inner side in the radial direction in the back cover molding space 52 sequentially flows into the projection molding space 53 and the flash land 54 while discharging the air remaining in the projection molding space 53.

この結果、金型装置から取り出されたシールリング１４ａには、外向鍔部２０ａの軸方向内側面の径方向中間部乃至外端部に亙る範囲（傾斜板部４２及び屈曲部４１の全面並びに平板部４０の外径側端部）を、それぞれ覆う状態で、背面覆部４５が形成される。又、背面覆部４５の内径側端部で且つ前記境界位置Ｘと軸方向に重畳する部分に、環状の突起部２９ａが形成される。更に、突起部２９ａの先端縁部に連続する状態で、例えば断面略五角形状のフラッシュ３０ａが形成される。尚、フラッシュ３０ａは、突起部２９ａの先端部の円周方向一部又は複数箇所に形成しても良いし、全周に亙り形成する事もできる。本例の場合には、この様な工程を経て製造されたシールリング１４ａに対して、フラッシュ３０ａを突起部２９ａの先端部から取り除く為の切除作業を行う。これにより、前記図２に示した様な、シールリング１４ａを得る。   As a result, the seal ring 14a taken out from the mold apparatus has a range extending from the radially intermediate portion to the outer end of the axially inner side surface of the outward flange portion 20a (the entire surface of the inclined plate portion 42 and the bent portion 41 and the flat plate). The back cover 45 is formed so as to cover the outer diameter side end of the portion 40. Further, an annular protrusion 29a is formed at the inner diameter side end of the back cover 45 and at a portion overlapping the boundary position X in the axial direction. Further, a flash 30a having a substantially pentagonal cross section, for example, is formed in a state of being continuous with the leading edge of the protrusion 29a. Note that the flash 30a may be formed at a part or a plurality of locations in the circumferential direction of the tip of the protrusion 29a, or may be formed over the entire circumference. In the case of this example, excision work for removing the flash 30a from the tip of the projection 29a is performed on the seal ring 14a manufactured through such a process. As a result, the seal ring 14a as shown in FIG. 2 is obtained.

以上の様な構成を有する本例の場合には、外輪２ａの軸方向外端面との間部分の密封性を十分に確保できるシールリング１４ａを低コストで得られる為、この様なシールリング１４ａを備えたシールリング付転がり軸受ユニット１ａのコスト低減を図れる。
即ち、本例の場合には、芯金１７ａの外向鍔部２０ａの外径寄り部分に、径方向外方に向かう程軸方向外方に向かう方向に傾斜した傾斜板部４２を設けている為、従来構造の様に薄板部２３（図９参照）を設けた場合と同様に、外向鍔部２０ａの軸方向内側に、外輪２ａの軸方向外端面との間部分を密封する為の背面覆部４５を形成する為の空間（背面覆部成形空間５２）を設ける事ができる。しかも、傾斜板部４２（及び屈曲部４１）は、コイニング加工ではなく、通常の曲げ加工により形成できる為、大型のプレス装置を用いずに、小型のプレス装置により加工する事が可能になる。従って、本例の場合には、外輪２ａの軸方向外端面との間部分の密封性を十分に確保できるシールリング１４ａを、低コストで造る事ができる。この結果、この様なシールリング１４ａを備えたシールリング付転がり軸受ユニット１ａのコスト低減を図れる。 In the case of this example having the above-described configuration, the seal ring 14a that can sufficiently ensure the sealing performance between the outer ring 2a and the axially outer end surface can be obtained at low cost. The cost reduction of the rolling bearing unit with a seal ring 1a provided with can be achieved.
That is, in the case of this example, the inclined plate portion 42 that is inclined in the axially outward direction toward the radially outward portion is provided at the portion near the outer diameter of the outward flange portion 20a of the metal core 17a. Similarly to the case where the thin plate portion 23 (see FIG. 9) is provided as in the conventional structure, the back cover for sealing the portion between the axially outer end surface of the outer ring 2a on the axially inner side of the outward flange portion 20a. A space for forming the portion 45 (back cover forming space 52) can be provided. In addition, since the inclined plate portion 42 (and the bent portion 41) can be formed not by coining but by ordinary bending, it can be processed by a small pressing device without using a large pressing device. Therefore, in the case of this example, the seal ring 14a that can sufficiently ensure the sealing performance between the outer ring 2a and the outer end surface in the axial direction can be manufactured at low cost. As a result, the cost of the rolling bearing unit with a seal ring 1a having such a seal ring 14a can be reduced.

又、本例の場合には、外向鍔部２０ａの外径寄り部分に存在する傾斜板部４２及び屈曲部４１を径方向外方に向かう程軸方向外方に向かう方向に傾斜させると共に、前記境界位置Ｘを突起部２９ａと軸方向に重畳させ、この突起部２９ａを背面覆部４５の内径側端部に設けている為、溶融ゴムを突起部成形空間５３へと効率良く供給する事ができる。
即ち、背面覆部形成空間５２の軸方向幅は、傾斜板部４２及び屈曲部４１の存在に基づいて径方向内側に向かう程狭くなる（断面形状がくさび状になる）為、溶融ゴムの流速は、径方向内側に移動する程上昇する。そして、この様に流速が上昇した溶融ゴムは、屈曲部４１の軸方向内側面と背面覆部成形空間５２の軸方向外側面に案内されて突起部成形空間５３に供給されるので、溶融ゴムは、背面覆部成形空間５２の内径側端部を塞いだ下型４８の外面（外周面）に勢い良く突き当たり、突起部成形空間５３に供給される。従って、本例の場合には、溶融ゴムを突起部成形空間５３へと効率良く供給する事ができ、突起部２９ａの成形性を良好にできる。 Further, in the case of this example, the inclined plate portion 42 and the bent portion 41 existing on the outer diameter portion of the outward flange portion 20a are inclined in the axially outward direction toward the radially outward direction, Since the boundary position X is overlapped with the protrusion 29a in the axial direction, and this protrusion 29a is provided at the inner diameter side end of the back cover 45, the molten rubber can be efficiently supplied to the protrusion molding space 53. it can.
That is, the axial width of the back cover forming space 52 becomes narrower toward the inner side in the radial direction based on the presence of the inclined plate portion 42 and the bent portion 41 (the cross-sectional shape becomes a wedge shape). Rises as it moves radially inward. Since the molten rubber whose flow rate has increased in this way is guided to the axially inner surface of the bent portion 41 and the axially outer surface of the back cover molding space 52 and supplied to the projection molding space 53, the molten rubber Vigorously strikes the outer surface (outer peripheral surface) of the lower die 48 that covers the inner diameter side end of the back cover molding space 52 and is supplied to the projection molding space 53. Therefore, in the case of this example, the molten rubber can be efficiently supplied to the projection forming space 53, and the moldability of the projection 29a can be improved.

又、突起部成形空間５３の先端部にフラッシュランド５４を設けている為、突起部２９ａ内に気泡が形成される事で、この突起部２９ａが成形不良になる事を有効に防止できる。しかも、本例の場合には、以下の理由により、フラッシュランド５４側に気泡（空気）を効率良く排出できる。
即ち、図４に示した様に、シールリング１４ａの加硫接着工程時には、外向鍔部２０ａの軸方向内側面を下型４８の支承面５１に強く押し付け、粘度の低い溶融ゴムが、背面覆部成形空間５２及び突起部成形空間５３よりも径方向内側に流れ出ない様にしている。この為、背面覆部形成空間５２及び突起部成形空間５３内に存在する気泡（空気）も、突起部成形空間５３よりも径方向内側には逃げられなくなる。ここで、背面覆部成形空間５２を径方向内側に移動する溶融ゴムは、屈曲部４１の軸方向内側面と背面覆部成形空間５２の軸方向外側面に接する部分では流速が遅く、軸方向中央部では流速が速くなる。背面覆部成形空間５２の軸方向外側面近傍の溶融ゴムは、突起部成形空間５３の入口側から奥部側に向かい、径方向外側から径方向内側に、流路断面の変化（断面積の増加）に伴って流速を落としながら斜め下方に流れる（図４中矢印α）。又、屈曲部４１の軸方向内側面近傍の溶融ゴムは、流路断面の変化が少ない為、流速をあまり落とす事なく、突起部成形空間５３を形成する下型４８の外面に突き当たる。一方、軸方向中央の溶融ゴムは、突起部成形空間５３を形成する下型４８の外面に勢い良く突き当たった後、径方向内側から径方向外側に斜め上方に流れる（図４中矢印β）。そして、この２つの流れ（矢印αと矢印β）は、突起部成形空間５３の奥部で交わるので、背面覆部成形空間５２内及び突起部成形空間５３内の空気を、フラッシュランド５４側に効率良く排出できる。 In addition, since the flash land 54 is provided at the tip of the protruding portion forming space 53, it is possible to effectively prevent the protruding portion 29a from being defectively formed by forming bubbles in the protruding portion 29a. In addition, in this example, bubbles (air) can be efficiently discharged to the flash land 54 side for the following reason.
That is, as shown in FIG. 4, during the vulcanization bonding process of the seal ring 14a, the inner surface in the axial direction of the outward flange portion 20a is strongly pressed against the support surface 51 of the lower mold 48, and the molten rubber having low viscosity is The part molding space 52 and the projection part molding space 53 are prevented from flowing out inward in the radial direction. For this reason, air bubbles (air) existing in the back cover forming space 52 and the protruding portion forming space 53 cannot escape from the protruding portion forming space 53 radially inward. Here, the molten rubber that moves inward in the radial direction in the back cover molding space 52 has a low flow velocity at the portion that is in contact with the inner side surface in the axial direction of the bent portion 41 and the outer side surface in the axial direction of the back cover molding space 52. In the center, the flow velocity becomes faster. The molten rubber in the vicinity of the outer surface in the axial direction of the back cover molding space 52 changes from the inlet side to the back side of the projection molding space 53 and changes from the radial outer side to the radial inner side (cross-sectional area change). As the flow rate increases, the flow proceeds obliquely downward (arrow α in FIG. 4). Further, the molten rubber in the vicinity of the inner side surface in the axial direction of the bent portion 41 has little change in the cross section of the flow path, so that it abuts against the outer surface of the lower mold 48 that forms the protruding portion forming space 53 without significantly reducing the flow velocity. On the other hand, the molten rubber at the center in the axial direction strikes the outer surface of the lower mold 48 forming the projection forming space 53 with a great force, and then flows obliquely upward from the radially inner side to the radially outer side (arrow β in FIG. 4). Since these two flows (arrow α and arrow β) intersect at the back of the projection molding space 53, the air in the back cover molding space 52 and the projection molding space 53 is moved to the flash land 54 side. It can be discharged efficiently.

更に、本例の場合には、下型４８の突起部２９ａの先端部を形成する部分の軸方向内側にフラッシュランド５４を設けている為、加硫接着成形したシールリング１４ａを下型４８から取り外すだけで、フラッシュ３０ａを切除する事が可能である。又、突起部２９ａの先端部にフラッシュ３０ａを設けている為、このフラッシュ３０ａを切除した際に生じるバリ部（残留部）が、突起部２９ａの密封性を阻害する事もない。   Further, in the case of this example, since the flash land 54 is provided on the inner side in the axial direction of the portion forming the tip portion of the projecting portion 29 a of the lower mold 48, the seal ring 14 a vulcanized and bonded is removed from the lower mold 48. The flash 30a can be excised simply by removing it. Further, since the flash 30a is provided at the tip of the protrusion 29a, the burr (residual part) generated when the flash 30a is cut does not hinder the sealing performance of the protrusion 29a.

［実施の形態の第２例］
本発明の実施の形態の第２例に就いて、図５〜７を参照しつつ説明する。本例の場合には、突起部２９ｂを背面覆部４５ａの径方向中間部に設け、背面覆部４５ａのうち突起部２９ｂよりも内径側に背面内径部５５を設けている。そして、この背面内径部５５を、芯金１７ａを構成する外向鍔部２０ａのうち、直線状の平板部４０の軸方向内側面と曲線状の屈曲部４１の軸方向内側面との境界位置（Ｒ止まり）Ｘと軸方向に重畳させている。 [Second Example of Embodiment]
A second example of the embodiment of the present invention will be described with reference to FIGS. In the case of this example, the protrusion 29b is provided in the radial intermediate portion of the back cover 45a, and the back inner diameter 55 is provided on the inner diameter side of the back cover 45a than the protrusion 29b. And this back inner diameter part 55 is the boundary position (in the outward flange part 20a which comprises the metal core 17a) between the axial inner side surface of the linear flat plate part 40 and the axial inner side surface of the curved bent part 41 ( R stop) It is overlapped with X in the axial direction.

又、背面内径部５５を、突起部２９ｂに近い外径寄り部分の厚肉部５６と、この厚肉部５６の径方向内側に隣接した状態で設けられ、この厚肉部５６よりも軸方向厚さ寸法の小さい薄肉部５７とから構成している。背面内径部５５は、図７の（Ａ）に示した様に、それぞれの軸方向厚さ寸法を一定とした厚肉部５６と薄肉部５７とを段差面５８を介して連続させる事により構成しても良いし、同図の（Ｂ）に示した様に、軸方向に関する厚さ寸法が径方向内側に向かう程徐々に（曲線的に又は直線的に）小さくなった薄肉部５７と、厚肉部５６とを直接連続させる事により構成しても良い。何れにしても、本例の場合には、薄肉部５７の軸方向内側面を、厚肉部５６の軸方向内側面よりも軸方向外側に位置（オフセット）させている。   Further, the back inner diameter portion 55 is provided in a state adjacent to the thick portion 56 near the outer diameter close to the protruding portion 29 b and the radially inner side of the thick portion 56, and more axial than the thick portion 56. The thin portion 57 has a small thickness. As shown in FIG. 7A, the rear inner diameter portion 55 is configured by connecting a thick portion 56 and a thin portion 57 having a constant axial thickness dimension through a step surface 58. Alternatively, as shown in (B) of the figure, the thin portion 57 that gradually decreases (curvely or linearly) as the thickness dimension in the axial direction goes radially inward, You may comprise by making the thick part 56 continue directly. In any case, in the case of this example, the inner side surface in the axial direction of the thin portion 57 is positioned (offset) outside the inner side surface in the axial direction of the thick portion 56.

以上の様な構成を有する本例のシールリング１４ｂを得るには、芯金１７ａにシール材１８ｂを加硫接着する際に、外向鍔部２０ａの軸方向内側に流動した溶融ゴムにより形成される薄肉部５７の軸方向内側面の内径側端縁部に、図６に破線で示した様なフラッシュ３０ｂを形成する。その後、下型４８から加硫接着成形したシールリング１４ｂを取り外す事で、このフラッシュ３０ｂを除去する。   In order to obtain the seal ring 14b of the present example having the above-described configuration, it is formed by molten rubber that flows inward in the axial direction of the outward flange portion 20a when the sealing material 18b is vulcanized and bonded to the core metal 17a. A flash 30b as shown by a broken line in FIG. 6 is formed on the inner diameter side edge of the inner side surface in the axial direction of the thin portion 57. Thereafter, the flash ring 30b is removed by removing the seal ring 14b formed by vulcanization and adhesion from the lower mold 48.

この為、本例の場合には、薄肉部５７の内径側端縁部に、フラッシュ３０ｂの残留部であるバリ部５９が残存してしまう可能性がある。但し、この様なバリ部５９が形成された場合にも、このバリ部５９は、軸方向内側面が厚肉部５６よりも軸方向外側にオフセットした薄肉部５７に形成される様にしている為、或いは、フラッシュ３０ｂの軸方向外側位置を、厚肉部５６よりも軸方向外側にしている為、バリ部５９の先端縁が、厚肉部５６の軸方向内側面よりも軸方向内方に突出しない様にする事ができる。又、バリ部５９の先端縁を、厚肉部５６の軸方向内側面よりも軸方向内方に突出させずに済む為、突起部２９ｂの突出量を小さく抑えた場合にも、この突起部２９ｂに十分な密封効果を発揮させる事ができる。   For this reason, in the case of this example, there is a possibility that the burr portion 59 which is the remaining portion of the flash 30 b remains at the inner diameter side edge portion of the thin portion 57. However, even when such a burr portion 59 is formed, the burr portion 59 is formed in the thin portion 57 whose axial inner side surface is offset outward in the axial direction from the thick portion 56. Alternatively, since the axially outer position of the flash 30b is positioned axially outside of the thick part 56, the tip edge of the burr part 59 is axially inward from the axial inner side surface of the thick part 56. It can be made not to protrude. Further, since the tip edge of the burr portion 59 does not need to protrude inward in the axial direction from the inner surface in the axial direction of the thick portion 56, this protrusion portion can be used even when the protrusion amount of the protrusion portion 29 b is kept small. 29b can exhibit a sufficient sealing effect.

更に本例の場合には、前記境界位置Ｘを突起部２９ｂよりも径方向内側に位置させている為、前述した実施の形態の第１例の場合に比べて、突起部２９ｂを形成する為の突起部成形空間５３（図４参照）と外向鍔部２０ａとの間の隙間を大きく確保できる。この為、溶融ゴムの流動性を高める事ができ、又、薄肉部５７の絞り効果で突起部２９ｂの成形圧力を上げる事ができるので、突起部２９ｂを小型化した場合にも、この突起部２９ｂに関する成形性を十分に確保できる。
その他の構成及び作用効果に就いては、前記実施の形態の第１例の場合と同様である。 Further, in the case of this example, the boundary position X is positioned radially inward from the protrusion 29b, so that the protrusion 29b is formed compared to the case of the first example of the above-described embodiment. A large gap can be secured between the projection forming space 53 (see FIG. 4) and the outward flange portion 20a. Therefore, the fluidity of the molten rubber can be increased, and the molding pressure of the projection 29b can be increased by the squeezing effect of the thin portion 57. Therefore, even when the projection 29b is downsized, this projection Sufficient moldability for 29b can be secured.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

本発明のシールリング付転がり軸受ユニットは、実施の形態の各例で説明した様な、車輪を回転自在に支持する為の車輪支持用の用途に限らず、その他の転がり軸受ユニットに適用する事もできる。又、車輪支持用の転がり軸受ユニットに適用する場合にも、従動輪用に限らず、駆動輪用の転がり軸受ユニットに適用する事もできる。又、本発明は、実施の形態の各例に示した構造を適宜組み合わせて実施する事もできる。   The rolling bearing unit with a seal ring of the present invention is not limited to the use for supporting the wheel for rotatably supporting the wheel as described in each example of the embodiment, but can be applied to other rolling bearing units. You can also. Also, when applied to a rolling bearing unit for supporting a wheel, the present invention can be applied not only to a driven wheel but also to a rolling bearing unit for a driving wheel. The present invention can also be implemented by appropriately combining the structures shown in the examples of the embodiment.

１、１ａ シールリング付転がり軸受ユニット
２、２ａ 外輪
３、３ａ ハブ
４、４ａ 転動体
５、５ａ 静止側フランジ
６ａ〜６ｄ 外輪軌道
７、７ａ ハブ本体
８、８ａ 内輪
９ ナット
１０ａ〜１０ｄ 内輪軌道
１１、１１ａ 保持器
１２、１２ａ 回転側フランジ
１３ スタッド
１４、１４ａ シールリング
１５、１５ａ 内部空間
１６、１６ａ カバー
１７、１７ａ 芯金
１８、１８ａ、１８ｂ シール材
１９、１９ａ 固定筒部
２０、２０ａ 外向鍔部
２１、２１ａ 内径支持部
２２ 除肉部
２３ 薄板部
２４、２４ａ 軸方向シールリップ
２５、２５ａ 径方向シールリップ
２６、２６ａ 径方向シールリップ
２７、２７ａ 外径側覆部
２８ 突出部
２９、２９ａ、２９ｂ 突起部
３０、３０ａ、３０ｂ フラッシュ
３１ 基半部
３２ 先半部
３３ 段部
３４ 円筒面部
３５ 凹曲面部
３６ 小径段部
３７ かしめ部
３８ 支持筒部
３９ 底板部
４０ 平板部
４１ 屈曲部
４２ 傾斜板部
４３ 補助リップ
４４ 表面覆部
４５、４５ａ 背面覆部
４６ 外周覆部
４７ 空間
４８ 下型
４９ 上型
５０ 抑え部
５１ 支承面
５２ 背面覆部成形空間
５３ 突起部成形空間
５４ フラッシュランド
５５ 背面内径部
５６ 厚肉部
５７ 薄肉部
５８ 段差面
５９ バリ部 DESCRIPTION OF SYMBOLS 1, 1a Rolling bearing unit with a seal ring 2, 2a Outer ring 3, 3a Hub 4, 4a Rolling element 5, 5a Static side flange 6a-6d Outer ring raceway 7, 7a Hub body 8, 8a Inner ring 9 Nut 10a-10d Inner ring raceway 11 , 11a Cage 12, 12a Rotating flange 13 Stud 14, 14a Seal ring 15, 15a Inner space 16, 16a Cover 17, 17a Core metal 18, 18a, 18b Sealing material 19, 19a Fixed cylinder part 20, 20a Outward flange part 21, 21a Inner diameter support portion 22 Thinning portion 23 Thin plate portion 24, 24a Axial seal lip 25, 25a Radial seal lip 26, 26a Radial seal lip 27, 27a Outer diameter side cover 28 Projection 29, 29a, 29b Projection 30, 30 a, 30 b Flash 31 Base half 32 Tip half 33 Part 34 cylindrical surface part 35 concave curved surface part 36 small diameter step part 37 caulking part 38 support cylinder part 39 bottom plate part 40 flat plate part 41 bent part 42 inclined plate part 43 auxiliary lip 44 surface covering part 45, 45a rear surface covering part 46 outer periphery covering part 47 Space 48 Lower mold 49 Upper mold 50 Holding part 51 Bearing surface 52 Back cover molding space 53 Projection molding space 54 Flash land 55 Back inner diameter part 56 Thick part 57 Thin part 58 Step part 59 Burr part

Claims (4)

使用時に回転する内径側軌道輪部材の外周面と使用時にも回転しない外径側軌道輪部材の内周面との間に存在する内部空間の軸方向片端開口部を塞ぐ為に使用されるもので、
芯金と、この芯金に支持された弾性材製のシール材とを備え、
この芯金は、金属板製で全体が円環状であり、前記外径側軌道輪部材の軸方向片端部に固定される固定筒部と、この固定筒部の軸方向片端部から径方向外方に向けて折れ曲がった外向鍔部とを有するもので、この外向鍔部は、前記芯金の中心軸に対し直交する方向に延出した平板部と、この平板部の径方向外側に隣接して設けられ、径方向外方に向かう程軸方向片方に向かう方向に曲線的に屈曲した屈曲部と、この屈曲部の径方向外側に隣接して設けられ、径方向外方に向かう程軸方向片方に向かう方向に傾斜した傾斜板部とを有しており、
前記シール材は、前記外向鍔部の周囲を覆った外径側覆部と、この外径側覆部のうち前記外向鍔部の軸方向他側を覆った背面覆部から軸方向他方に突出する状態で設けられ、前記外径側軌道輪部材の軸方向片端面と接触する突起部とを有するものであり、
前記平板部の軸方向他側面と前記屈曲部の軸方向他側面との境界位置が、前記突起部又は前記背面覆部のうちこの突起部よりも内径側に存在する部分と軸方向に重畳している、
シールリング。 Used to block the axial one-end opening of the internal space between the outer peripheral surface of the inner ring-side bearing ring member that rotates during use and the inner peripheral surface of the outer diameter-side bearing ring member that does not rotate during use so,
Comprising a cored bar and a sealing material made of an elastic material supported by the cored bar,
The metal core is made of a metal plate and has an annular shape as a whole, and a fixed cylinder portion fixed to one end portion in the axial direction of the outer diameter side race ring member, and a radially outer side from the one end portion in the axial direction of the fixed cylinder portion. An outward flange portion bent toward the direction, and the outward flange portion is adjacent to a flat plate portion extending in a direction perpendicular to the central axis of the cored bar and radially outward of the flat plate portion. A bent portion that is curved in a direction toward one axial direction as it goes radially outward, and is provided adjacent to a radially outer side of this bent portion, and an axial direction that goes radially outward And an inclined plate portion inclined in a direction toward one side,
The sealing material protrudes in the other axial direction from an outer diameter side cover that covers the periphery of the outward flange, and a back cover that covers the other side of the outer flange in the axial direction of the outer diameter side cover. Provided with a protruding portion that is in contact with the one axial end surface of the outer diameter side bearing ring member,
The boundary position between the other side surface in the axial direction of the flat plate portion and the other side surface in the axial direction of the bent portion overlaps in the axial direction with a portion of the projection portion or the back cover portion that is on the inner diameter side of the projection portion. ing,
Seal ring. 前記背面覆部の内径側端部に前記突起部が設けられており、前記境界位置が、この突起部と軸方向に重畳している、請求項１に記載したシールリング。   The seal ring according to claim 1, wherein the protrusion is provided at an inner diameter side end of the back cover, and the boundary position overlaps with the protrusion in the axial direction. 前記境界位置が、前記背面覆部のうち前記突起部よりも内径側に存在する背面内径部と軸方向に重畳しており、
前記背面内径部は、厚肉部と、この厚肉部の径方向内側に隣接して設けられ、この厚肉部よりも軸方向厚さ寸法が小さい薄肉部とを有しており、この薄肉部の軸方向他側面が前記厚肉部の軸方向他側面よりも軸方向片側に位置している、請求項１に記載したシールリング。 The boundary position is overlapped in the axial direction with the back inner diameter part existing on the inner diameter side of the protrusion in the back cover part,
The back inner diameter portion has a thick portion and a thin portion provided adjacent to the radially inner side of the thick portion and having a smaller axial thickness than the thick portion. The seal ring according to claim 1, wherein an axial other side surface of the portion is located on one axial side than an axial other side surface of the thick portion. 内周面に外輪軌道を有し、使用時にも回転しない、前記外径側軌道輪部材である外輪と、外周面のうちでこの外輪軌道と対向する部分に内輪軌道を有し、使用時に回転する、前記内径側軌道輪部材であるハブと、これら外輪軌道と内輪軌道との間に転動自在に設けられた複数個の転動体と、前記外輪の内周面と前記ハブの外周面との間に存在する内部空間の軸方向外端開口部を塞ぐシールリングとを備えたシールリング付転がり軸受ユニットであって、
前記シールリングが、請求項１〜３のうちの何れか１項に記載したシールリングである事を特徴とするシールリング付転がり軸受ユニット。
An outer ring raceway on the inner peripheral surface that does not rotate during use, and the outer ring that is the outer diameter side race ring member, and an outer ring has an inner ring raceway in a portion facing the outer ring raceway, and rotates during use. A hub that is the inner ring raceway member, a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway, an inner peripheral surface of the outer ring, and an outer peripheral surface of the hub. A rolling bearing unit with a seal ring, comprising a seal ring that closes the axially outer end opening of the internal space existing between
A rolling bearing unit with a seal ring, wherein the seal ring is the seal ring according to any one of claims 1 to 3.
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DE202019104178U1 (en) 2018-07-30 2019-10-29 Nsk Ltd. Roller bearing unit for wheel support
JP2021025532A (en) * 2019-07-31 2021-02-22 光洋シーリングテクノ株式会社 Sealing device

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JPWO2021049158A1 (en) * 2019-09-13 2021-03-18

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JP2015113896A (en) * 2013-12-11 2015-06-22 日本精工株式会社 Seal ring, and seal ring-provided rolling bearing unit for supporting wheel

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DE202019104178U1 (en) 2018-07-30 2019-10-29 Nsk Ltd. Roller bearing unit for wheel support
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JP2021025532A (en) * 2019-07-31 2021-02-22 光洋シーリングテクノ株式会社 Sealing device

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