JP2018119598A

JP2018119598A - Bearing sealing device

Info

Publication number: JP2018119598A
Application number: JP2017011005A
Authority: JP
Inventors: 勢野　洋嗣; Hirotsugu Seno; 洋嗣勢野
Original assignee: Uchiyama Manufacturing Corp
Current assignee: Uchiyama Manufacturing Corp
Priority date: 2017-01-25
Filing date: 2017-01-25
Publication date: 2018-08-02

Abstract

PROBLEM TO BE SOLVED: To provide a bearing sealing device which suppresses foreign substances such as muddy water and the like from reaching a radial lip, and in which a seal function is maintained for a long time.SOLUTION: A bearing sealing device is constituted by: a metallic ring 12 fitted in an inner diameter side member 5; and a seal member 13 fitted in an outer diameter side member 2. The metallic ring 12 includes: a first fitting cylindrical part 121 fitted in an outer peripheral surface 4b of the inner diameter side member 4(5); a first circular ring part 122 extending to an outer diameter side from an axial direction outside end part 121a of the first fitting cylindrical part 121; and the first circular ring part 122 extending to the outer diameter side and a bent circular ring part 123. The seal member 13 has: a core bar 14 fitted in an inner peripheral surface 2b of the outer diameter side member 2; and a radial lip 151 coming into contact with the inner diameter side member 5 and an axial lip 152 coming into contact with the first circular ring part 122. The bent circular ring part 123 is located between the radial lip 151 and the axial lip 152, and outer diameter direction height h from the first fitting cylindrical part 121 of the bent circular ring part 123 is larger than thickness d of the first fitting cylindrical part 121.SELECTED DRAWING: Figure 2

Description

本発明は、例えば、自動車等の車輪支持部の軸受装置に用いられる軸受密封装置に関し、さらに詳しくは、相対的に同軸回転可能な外径側部材と内径側部材との間の環状空間に装着されて当該環状空間を密封する軸受密封装置に関する。 The present invention relates to a bearing sealing device used for a bearing device of a wheel support portion of, for example, an automobile, and more specifically, is mounted in an annular space between an outer diameter side member and an inner diameter side member that can relatively rotate coaxially. The present invention relates to a bearing sealing device that seals the annular space.

前記のような密封装置としては、内径側部材の外周面に嵌合されるスリンガ（これと同等の部材も含む）と、外径側部材の内周面に嵌合される芯金及び該芯金に固着されて前記スリンガに接触するシールリップを有するシール部材とが組み合わさって構成される軸受密封装置が多く用いられている（例えば、特許文献１〜３参照）。このような軸受密封装置は、内径側部材又は外径側部材の軸回転に伴うシールリップのスリンガに対する相対摺接によって、外部からの環状空間（軸受空間）内への泥水等の浸入を阻止し、また、軸受空間内に充填されるグリース等の外部漏出を阻止するよう設計される。 The sealing device as described above includes a slinger (including a member equivalent thereto) fitted to the outer peripheral surface of the inner diameter side member, a core bar fitted to the inner peripheral surface of the outer diameter side member, and the core Many bearing sealing devices are used which are combined with a seal member having a seal lip that is fixed to gold and contacts the slinger (see, for example, Patent Documents 1 to 3). Such a bearing sealing device prevents intrusion of muddy water or the like from the outside into the annular space (bearing space) by the relative sliding contact of the seal lip with the slinger associated with the shaft rotation of the inner diameter side member or the outer diameter side member. Also, it is designed to prevent external leakage of grease or the like filled in the bearing space.

特許文献１に記載された密封装置は、スリーブの鍔部に弾性摺接するアキシャルリップと、スリーブの筒部に弾性摺接するラジアルリップと、内輪の外周面に弾性摺接するラジアルリップとを備えている。また、特許文献２に記載された密封装置は、スリンガ環状部に弾性摺接するアキシャルリップと、スリンガ円筒部に弾性摺接するラジアルリップと、内輪の外周面に弾性摺接するラジアルリップとを備えている。さらに、特許文献３に記載された密封装置は、摺動環（スリンガ）の円盤部に弾性摺接するアキシャルリップと、内輪に弾性摺接するラジアルリップとを備えている。 The sealing device described in Patent Document 1 includes an axial lip that is in elastic sliding contact with the collar portion of the sleeve, a radial lip that is elastically sliding in contact with the cylindrical portion of the sleeve, and a radial lip that is in elastic sliding contact with the outer peripheral surface of the inner ring. . The sealing device described in Patent Document 2 includes an axial lip that elastically contacts the slinger annular portion, a radial lip that elastically contacts the slinger cylindrical portion, and a radial lip that elastically contacts the outer peripheral surface of the inner ring. . Furthermore, the sealing device described in Patent Document 3 includes an axial lip that is in elastic sliding contact with the disk portion of the sliding ring (slinger) and a radial lip that is elastically sliding in contact with the inner ring.

実用新案登録第２５８９４７７号公報Utility Model Registration No. 2589477 特開２００７−２７０８５９号公報JP 2007-270859 A 特許第４７３５７９８号公報Japanese Patent No. 4735798

前記のような軸受密封装置の場合、アキシャルリップが外部からの泥水等の浸入を阻止する主体とされる。しかし、過酷な条件下に晒される自動車用の軸受密封装置の場合、アキシャルリップとスリンガとの相対摺接部に泥水が至り、経時的にこの相対摺接部に泥水に含まれる塵埃等の異物が噛み込み、アキシャルリップの先端部が摩耗することがある。このような摩耗が進行すると、泥水がさらに密封装置内に浸入し、ラジアルリップとスリンガ或いは内輪との相対摺接部に至り、ラジアルリップの先端部も摩耗し、その結果、泥水が軸受空間内にまで浸入し、本来の密封機能が果たせなくなることにもなる。したがって、アキシャルリップの前記相対摺接部を泥水が通過したとしても、ラジアルリップの前記相対摺接部にできるだけ泥水が到達し難くなるような構造が望まれる。 In the case of the bearing sealing device as described above, the axial lip is mainly used to prevent intrusion of muddy water and the like from the outside. However, in the case of a bearing sealing device for an automobile that is exposed to harsh conditions, muddy water reaches the relative sliding contact portion between the axial lip and the slinger. May bite and the tip of the axial lip may wear. When such wear progresses, the muddy water further penetrates into the sealing device, reaches the relative sliding contact portion between the radial lip and the slinger or the inner ring, and the tip of the radial lip also wears. It will also penetrate to the point where the original sealing function cannot be performed. Therefore, even if muddy water passes through the relative sliding contact portion of the axial lip, a structure that makes it difficult for the muddy water to reach the relative sliding contact portion of the radial lip is desired.

特許文献１に記載された密封装置の場合、アキシャルリップの摺接部を通過した泥水が弾性リップ（ラジアルリップ）４とスリーブ（スリンガ）７との摺接部に到達することが予想される。弾性リップ４とスリーブ７との摺接部に泥水が到達すると、さらにこの摺接部を通過して弾性リップ５と内輪１２との摺接部に至ることも起こり得る。また、特許文献２に記載された密封装置の場合も、アキシャルリップ１６とスリンガ環状部１２との摺接部を通過した泥水はメインリップ（ラジアルリップ）１４とスリンガ円筒部１１との摺接部に至ることは不可避である。そのため、この部分でのメインリップ１４に摩耗が生じることが懸念される。さらに、特許文献３に記載された密封装置の場合、摺動環（スリンガ）３における内周嵌合部３１の円錐形状部３４が、メインリップ（アキシャルリップ）２２と内周サブリップ（ラジアルリップ）２３との間に位置し、且つ、円錐形状部３４とシール本体２との間に内周ラビリンス隙間Ｌｒ_１が形成されている。そのため、メインリップ２３と円盤部３２との摺接部を通過した泥水は、内周サブリップ２３と摺動環３の内周嵌合部２３との摺接部に到達し難いと考えられる。しかし、円錐形状部３４が軸受空間側に向く円錐形状であることから、この部分に至った泥水はその先端部を乗り越え内周ラビリンス隙間Ｌｒ_１を経て内周サブリップ２３に至ることも起こり得る。そのため、ラジアルリップに泥水が到達し難くする構造としては、まだ充分とは言えないと考えられる。 In the case of the sealing device described in Patent Document 1, it is expected that the muddy water that has passed through the sliding contact portion of the axial lip reaches the sliding contact portion between the elastic lip (radial lip) 4 and the sleeve (slinger) 7. When muddy water reaches the sliding contact portion between the elastic lip 4 and the sleeve 7, it may further pass through this sliding contact portion and reach the sliding contact portion between the elastic lip 5 and the inner ring 12. Also in the case of the sealing device described in Patent Document 2, the muddy water that has passed through the sliding contact portion between the axial lip 16 and the slinger annular portion 12 is the sliding contact portion between the main lip (radial lip) 14 and the slinger cylindrical portion 11. It is unavoidable to reach. For this reason, there is a concern that the main lip 14 is worn at this portion. Further, in the case of the sealing device described in Patent Document 3, the conical shape portion 34 of the inner peripheral fitting portion 31 in the sliding ring (slinger) 3 includes a main lip (axial lip) 22 and an inner peripheral sub lip (radial lip). The inner circumferential labyrinth gap Lr ₁ is formed between the conical portion 34 and the seal body 2. Therefore, it is considered that the muddy water that has passed through the sliding contact portion between the main lip 23 and the disk portion 32 does not easily reach the sliding contact portion between the inner peripheral sub-lip 23 and the inner peripheral fitting portion 23 of the sliding ring 3. However, since the conical portion 34 has a conical shape facing the bearing space side, the muddy water reaching this portion may get over the tip and reach the inner peripheral sub lip 23 via the inner peripheral labyrinth gap Lr ₁ . For this reason, it is still not considered sufficient as a structure that makes it difficult for muddy water to reach the radial lip.

本発明は、前記実情に鑑みなされたもので、簡単な構造でありながら、ラジアルリップへの泥水等の異物の到達を抑え、シール機能が長く維持される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 has an object to provide a bearing sealing device that has a simple structure but prevents the arrival of foreign matters such as muddy water to the radial lip and maintains a long sealing function. Yes.

本発明に係る軸受密封装置は、相対的に同軸回転する内径側部材と外径側部材との間の環状空間を密封する軸受密封装置であって、前記内径側部材に嵌合される金属環と、前記外径側部材に嵌合されるシール部材とが組み合わさって構成され、前記金属環は、前記内径側部材の外周面に嵌合される第１嵌合円筒部と、該第１嵌合円筒部の軸方向外側端部から外径側に延びる第１円輪部と、前記第１嵌合円筒部の軸方向内側端部から外径側に屈曲された屈曲円輪部と、を備え、前記シール部材は、前記外径側部材の内周面に嵌合される第２嵌合円筒部及び該第２嵌合円筒部の軸方向内側端部から内径側に延びる第２円輪部を有する芯金と、前記内径側部材に接触するラジアルリップ及び前記第１円輪部に接触するアキシャルリップを有して前記芯金に固着された弾性部材と、を備え、前記屈曲円輪部は、前記ラジアルリップと前記アキシャルリップとの間に位置し、当該屈曲円輪部の前記第１嵌合円筒部からの外径方向高さが当該第１嵌合円筒部の厚さより大きいことを特徴とする。 A bearing sealing device according to the present invention is a bearing sealing device that seals an annular space between an inner diameter side member and an outer diameter side member that rotate relatively coaxially, and a metal ring that is fitted to the inner diameter side member. And a seal member fitted to the outer diameter side member, and the metal ring includes a first fitting cylindrical portion fitted to the outer peripheral surface of the inner diameter side member, and the first A first annular portion extending from the outer end in the axial direction of the fitting cylindrical portion to the outer diameter side, a bent annular portion bent from the inner end in the axial direction of the first fitting cylindrical portion to the outer diameter side, The seal member includes a second fitting cylindrical portion fitted to the inner peripheral surface of the outer diameter side member, and a second circle extending from the axially inner end of the second fitting cylindrical portion toward the inner diameter side. A metal core having a ring portion, a radial lip that contacts the inner diameter side member, and an axial lip that contacts the first circular ring portion; An elastic member fixed to gold, and the bent annular portion is located between the radial lip and the axial lip, and an outer diameter of the bent annular portion from the first fitting cylindrical portion The height in the direction is larger than the thickness of the first fitting cylindrical portion.

本発明の軸受密封装置によれば、内径側部材及び外径側部材のいずれか一方の軸回転に伴い、アキシャルリップが金属環の第１円輪部に相対摺接する。これによって、外部から当該軸受密封装置内への泥水等の異物（以下、泥水等と言う）の浸入が阻止される。しかし、前記軸回転中に、アキシャルリップの第１円輪部に対する接触度合が変化したり、或いは、アキシャルリップの先端部が経時的に摩耗したりすることがあり、そのため、泥水等がアキシャルリップの前記摺接部を通過することがある。このようにアキシャルリップの摺接部を通過した泥水等は、屈曲円輪部によって堰き止められて、屈曲円輪部、第１嵌合円筒部及び第１円輪部で形成される溝状空間に一時的に滞留する。この溝状空間は環状であるから、泥水等は一時的に滞留するも溝状空間内を下方に流れて前記アキシャルリップの摺接部を経て速やかに排出される。したがって、当該軸受密封装置内に泥水等が一時的に浸入しても、泥水等がラジアルリップと内径側部材との摺接部に到達することは少なく、泥水等の当該摺接部への噛み込みによるラジアルリップの先端部の摩耗が生じることが抑制される。しかも、屈曲円輪部の第１嵌合円筒部からの外径方向高さが第１嵌合円筒部の厚さより大きいから、屈曲円輪部の前記堰止め機能が効果的に発揮され、当該軸受密封装置のシール機能が長く維持され、長寿命化が図られる。因みに、屈曲円輪部の前記高さが第１嵌合円筒部の厚さより小さくなると、前記泥水等の堰止め機能が減退する傾向となる。 According to the bearing sealing device of the present invention, the axial lip comes into relative sliding contact with the first annular portion of the metal ring as the shaft of either the inner diameter side member or the outer diameter side member rotates. As a result, entry of foreign matter such as muddy water (hereinafter referred to as muddy water) into the bearing sealing device from the outside is prevented. However, the degree of contact of the axial lip with the first annular portion may change during the rotation of the shaft, or the tip of the axial lip may wear over time. May pass through the sliding contact portion. Thus, the muddy water or the like that has passed through the sliding contact portion of the axial lip is blocked by the bent annular portion, and is formed into a groove-like space formed by the bent annular portion, the first fitting cylindrical portion, and the first annular portion. Stays temporarily. Since this groove-shaped space is annular, mud water or the like temporarily stays but flows downward in the groove-shaped space and is quickly discharged through the sliding contact portion of the axial lip. Therefore, even if muddy water or the like temporarily enters the bearing sealing device, the muddy water or the like hardly reaches the sliding contact portion between the radial lip and the inner diameter side member, and the muddy water or the like is caught in the sliding contact portion. It is possible to suppress the wear of the distal end portion of the radial lip due to the insertion. Moreover, since the outer diameter direction height of the bent ring portion from the first fitting cylindrical portion is larger than the thickness of the first fitting cylindrical portion, the damming function of the bent ring portion is effectively exhibited, The seal function of the bearing sealing device is maintained for a long time, and the service life is extended. Incidentally, when the height of the bent ring portion is smaller than the thickness of the first fitting cylindrical portion, the function of blocking the muddy water or the like tends to decline.

本発明の軸受密封装置において、前記金属環は、第１円輪部の外径側端部から軸方向内方に延びる円筒部をさらに備えているものとしてもよい。
これによれば、外部からアキシャルリップの前記摺接部に至る泥水等の浸入経路が実質的に長くなり、ラジアルリップにおける前記摺接部への泥水等の到達がより生じ難くなる。 In the bearing sealing device of the present invention, the metal ring may further include a cylindrical portion extending inward in the axial direction from the outer diameter side end portion of the first annular portion.
According to this, the infiltration path of muddy water or the like from the outside to the sliding contact portion of the axial lip becomes substantially longer, and it becomes more difficult for the muddy water or the like to reach the sliding contact portion of the radial lip.

本発明の軸受密封装置において、前記金属環における前記屈曲円輪部の前記外径方向高さを０．６ｍｍ以上としてもよい。
これによれば、通常前記金属環は板厚が０．６ｍｍの鋼板によって作製されることが多く、したがって、屈曲円輪部の前記外径方向高さを０．６ｍｍ以上としているので、自ずと第１嵌合円筒部の厚さより大とされ、前記泥水等の堰止め機能が的確に発揮される。 In the bearing sealing device of the present invention, the height in the outer diameter direction of the bent ring portion in the metal ring may be 0.6 mm or more.
According to this, the metal ring is usually made of a steel plate having a thickness of 0.6 mm. Therefore, the height of the bent ring portion in the outer diameter direction is set to 0.6 mm or more. The thickness is larger than the thickness of one fitting cylindrical portion, and the function of blocking the muddy water and the like is accurately exhibited.

本発明の軸受密封装置において、前記金属環における前記屈曲円輪部の厚さを前記第１嵌合円筒部の厚さより小さくしてもよい。
これによれば、屈曲円輪部は、第１嵌合円筒部の延長部分を板金加工することによって屈曲形成されるので、この板金加工がし易くなる。因みに、屈曲円輪部の厚さが前記第１嵌合円筒部の厚さより大きいと、前記板金加工がし難くなる。 In the bearing sealing device of the present invention, the thickness of the bent ring portion in the metal ring may be smaller than the thickness of the first fitting cylindrical portion.
According to this, the bent ring portion is bent and formed by subjecting the extended portion of the first fitting cylindrical portion to sheet metal processing, so that this sheet metal processing becomes easy. Incidentally, if the thickness of the bent ring portion is larger than the thickness of the first fitting cylindrical portion, the sheet metal processing becomes difficult.

本発明の軸受密封装置において、前記金属環における前記屈曲円輪部の前記第１嵌合円筒部に対する屈曲角度が８０°以上且つ９５°以下としてもよい。
これによれば、屈曲円輪部の泥水等の堰止め機能が効果的に発揮される。因みに、屈曲円輪部の前記第１嵌合円筒部に対する屈曲角度が、８０°未満の場合前記泥水等の一時的な滞留時間が長くなる傾向となり、また、９５°を超えると前記堰止め機能が減退する傾向となる。 In the bearing sealing device of the present invention, a bending angle of the bent ring portion of the metal ring with respect to the first fitting cylindrical portion may be 80 ° or more and 95 ° or less.
According to this, a damming function such as muddy water in the bent ring portion is effectively exhibited. Incidentally, when the bending angle of the bent ring portion with respect to the first fitting cylindrical portion is less than 80 °, the temporary residence time of the muddy water or the like tends to be long, and when it exceeds 95 °, the damming function is increased. Tend to decline.

本発明の軸受密封装置において、前記金属環における前記屈曲円輪部と前記弾性部材との最小隙間を０．４ｍｍ以上としてもよい。
これによれば、不可避的な軸受密封装置の設計公差や内径側部材および外径側部材の偏心等があっても、内径側部材と外径側部材との相対的軸回転の際に、屈曲円輪部と弾性部材とが接触する懸念がない。因みに、屈曲円輪部の外径側端部と弾性部材との隙間が０．４ｍｍ未満になると、前記接触が生じ易くなる傾向となる。 In the bearing sealing device of the present invention, a minimum gap between the bent ring portion and the elastic member in the metal ring may be 0.4 mm or more.
According to this, even if there is an unavoidable design tolerance of the bearing sealing device and eccentricity of the inner diameter side member and the outer diameter side member, the inner diameter side member and the outer diameter side member are bent during relative rotation. There is no concern that the annular portion and the elastic member come into contact with each other. Incidentally, when the clearance between the outer diameter side end of the bent ring portion and the elastic member is less than 0.4 mm, the contact tends to occur.

本発明の軸受密封装置によれば、簡単な構造でありながら、ラジアルリップへの泥水等の異物の到達を抑え、シール機能が長く維持される。 According to the bearing sealing device of the present invention, while having a simple structure, the arrival of foreign matter such as muddy water to the radial lip is suppressed, and the sealing function is maintained for a long time.

本発明に係る軸受密封装置が適用される軸受装置の一例を示す概略的縦断面図である。It is a schematic longitudinal cross-sectional view which shows an example of the bearing apparatus with which the bearing sealing apparatus which concerns on this invention is applied. 図１のＸ部の拡大図であって、本発明に係る軸受密封装置の一実施形態を示す図である。It is an enlarged view of the X section of Drawing 1, and is a figure showing one embodiment of the bearing sealing device concerning the present invention. 同実施形態の軸受密封装置の性能試験の結果を示す図である。It is a figure which shows the result of the performance test of the bearing sealing device of the embodiment. 本発明に係る軸受密封装置の別の実施形態を示す図２と同様図である。It is a figure similar to FIG. 2 which shows another embodiment of the bearing sealing device which concerns on this invention. 本発明に係る軸受密封装置のさらに別の実施形態を示す図２と同様図である。It is the same figure as FIG. 2 which shows another embodiment of the bearing sealing device which concerns on this invention. 同実施形態の変形例を示す図２と同様図である。It is the same figure as FIG. 2 which shows the modification of the embodiment.

以下、本発明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（不図示）を軸回転可能に支持する軸受装置１を示す。この軸受装置１は、駆動輪用のハブベアリングであって、大略的に、外輪（外径側部材）２と、ハブ輪３と、ハブ輪３の車体側に嵌合一体とされる内輪部材４と、外輪２とハブ輪３及び内輪部材４との間に介装される２列の転動体（ボール）６…とを含んで構成される。この例では、ハブ輪３及び内輪部材４が内輪（内径側部材）５を構成し、外輪２は、自動車の車体（不図示）に固定される。また、ハブ輪３にはドライブシャフト７が同軸的にスプライン嵌合され、ドライブシャフト７は等速ジョイント８を介して不図示の駆動源（駆動伝達部）に連結される。ドライブシャフト７はナット９によって、ハブ輪３と一体化され、ハブ輪３のドライブシャフト７からの抜脱が防止されている。回転側である内輪５（ハブ輪３及び内輪部材４）は固定側である外輪２に対して、軸Ｌ回りに同軸回転可能とされ、外輪２と、内輪５との間に環状空間（軸受空間）Ｓが形成される。環状空間としての軸受空間Ｓ内には、２列の転動体６…が、リテーナ６ａに保持された状態で、外輪２の軌道輪２ａ、ハブ輪３の軌道輪３ａ及び内輪部材４の軌道輪４ａを転動可能に介装されている。ハブ輪３は、円筒形状のハブ輪本体３０と、ハブ輪本体３０より立上基部３１を介して径方向外側に延出されたハブフランジ３２とを有し、ハブフランジ３２にボルト３３及び不図示のナットによって車輪が取付固定される。本明細書において、軸Ｌ方向に沿って車輪に向く側（図１において左側を向く側）を車輪側、車体に向く側（同右側を向く側）を車体側と言う。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a bearing device 1 that supports a wheel (not shown) of an automobile so as to be axially rotatable. This bearing device 1 is a hub bearing for a drive wheel, and is roughly an outer ring (outer diameter side member) 2, a hub ring 3, and an inner ring member fitted and integrated with the hub wheel 3 on the vehicle body side. 4 and two rows of rolling elements (balls) 6... Interposed between the outer ring 2, the hub ring 3, and the inner ring member 4. In this example, the hub wheel 3 and the inner ring member 4 constitute an inner ring (inner diameter side member) 5, and the outer ring 2 is fixed to a vehicle body (not shown) of an automobile. A drive shaft 7 is coaxially spline-fitted to the hub wheel 3, and the drive shaft 7 is connected to a drive source (drive transmission unit) (not shown) via a constant velocity joint 8. The drive shaft 7 is integrated with the hub wheel 3 by a nut 9 to prevent the hub wheel 3 from being detached from the drive shaft 7. The inner ring 5 (the hub ring 3 and the inner ring member 4) on the rotating side can be coaxially rotated around the axis L with respect to the outer ring 2 on the fixed side, and an annular space (bearing) is formed between the outer ring 2 and the inner ring 5. A space) S is formed. In the bearing space S as an annular space, two rows of rolling elements 6 are held by the retainer 6a, and the race ring 2a of the outer ring 2, the race ring 3a of the hub ring 3, and the race ring of the inner ring member 4 are arranged. 4a is interposed so that it can roll. The hub ring 3 includes a cylindrical hub ring main body 30 and a hub flange 32 extending radially outward from the hub ring main body 30 via a rising base portion 31. The wheel is attached and fixed by the illustrated nut. In this specification, the side facing the wheel along the axis L direction (the side facing the left side in FIG. 1) is referred to as the wheel side, and the side facing the vehicle body (the side facing the right side) is referred to as the vehicle body side.

軸受空間Ｓの軸Ｌ方向に沿った両端部であって、外輪２とハブ輪３との間、及び、外輪２と内輪部材４との間には、ベアリングシール１０，１１が装着され、軸受空間Ｓの軸Ｌ方向に沿った両端部が密封される。これによって、軸受空間Ｓ内への泥水等の浸入や軸受空間Ｓ内に充填される潤滑剤（グリース等）の外部への漏出が防止される。 Bearing seals 10 and 11 are mounted at both ends of the bearing space S along the axis L direction, between the outer ring 2 and the hub ring 3 and between the outer ring 2 and the inner ring member 4. Both end portions along the axis L direction of the space S are sealed. This prevents intrusion of muddy water or the like into the bearing space S and leakage of the lubricant (grease or the like) filled in the bearing space S to the outside.

図２は、本発明に係る軸受密封装置の一実施形態を示し、本実施形態では、ベアリングシール１０，１１のうち、車体側のベアリングシール１１に本発明に係る軸受密封装置が適用された例を示している。本実施形態のベアリングシール（軸受密封装置）１１は、内輪（内径側部材）５に嵌合されるスリンガ（金属環）１２と、外輪（外径側部材）２に嵌合されるシール部材１３とが組み合わさって構成される。スリンガ１２は、内径側部材としての内輪部材４（内輪５）の外周面４ｂに嵌合される第１嵌合円筒部１２１と、第１嵌合円筒部１２１の車体側端部（軸Ｌ方向外側端部）１２１ａから外径側に延びる第１円輪部１２２と、第１嵌合円筒部１２１の車輪側端部（軸Ｌ方向内側端部）１２１ｂから外径側に屈曲された屈曲円輪部１２３とを備える。また、シール部材１３は、外輪２の内周面２ｂに嵌合される第２嵌合円筒部１４１及び第２嵌合円筒部１４１の車輪側端部（軸Ｌ方向内側端部）１４１ａから内径側に延びる第２円輪部１４２を有する芯金１４と、内輪部材４の外周面４ｂに接触するラジアルリップ１５１及び第１円輪部１２２の車輪側面１２２ａに接触するアキシャルリップ１５２を有して芯金１４に固着された弾性部材１５とを備える。そして、スリンガ１２の屈曲円輪部１２３は、ラジアルリップ１５１とアキシャルリップ１５２との間に位置するように形成され、屈曲円輪部１２３の第１嵌合円筒部１２１からの外径方向高さｈが第１嵌合円筒部１２１の厚さｄより大とされている。加えて、本実施形態では、屈曲円輪部１２３が第２円輪部１４２より軸Ｌ方向の車体側に位置し、且つ、屈曲円輪部１２３の外径側部分が第２円輪部１４２の車体側面１４２ｃに軸Ｌ方向に重なる位置に及ぶように形成されている。そして、図例のラジアルリップ１５１及びアキシャルリップ１５２は、それぞれ内輪部材４の外周面４ｂ及び第１円輪部１２２の車輪側面１２２ａに、弾性変形を伴い（しめ代をもって）接触するよう形成されており、それぞれの２点鎖線は弾性変形前の原形を示している。 FIG. 2 shows an embodiment of a bearing sealing device according to the present invention. In this embodiment, the bearing sealing device according to the present invention is applied to the bearing seal 11 on the vehicle body side of the bearing seals 10 and 11. Is shown. The bearing seal (bearing sealing device) 11 of this embodiment includes a slinger (metal ring) 12 fitted to the inner ring (inner diameter side member) 5 and a seal member 13 fitted to the outer ring (outer diameter side member) 2. And is composed. The slinger 12 includes a first fitting cylindrical portion 121 fitted to the outer peripheral surface 4b of the inner ring member 4 (inner ring 5) as an inner diameter side member, and a vehicle body side end portion of the first fitting cylindrical portion 121 (in the axis L direction). A first circular ring portion 122 extending from the outer end portion 121a to the outer diameter side, and a bent circle bent from the wheel side end portion (the inner end portion in the axis L direction) 121b of the first fitting cylindrical portion 121 to the outer diameter side. And an annular portion 123. Further, the seal member 13 has an inner diameter from the second fitting cylindrical portion 141 fitted to the inner peripheral surface 2b of the outer ring 2 and the wheel side end portion (the inner end portion in the axis L direction) 141a of the second fitting cylindrical portion 141. A metal core 14 having a second annular portion 142 extending to the side, a radial lip 151 that contacts the outer peripheral surface 4 b of the inner ring member 4, and an axial lip 152 that contacts the wheel side surface 122 a of the first annular portion 122. And an elastic member 15 fixed to the cored bar 14. The bent ring portion 123 of the slinger 12 is formed so as to be positioned between the radial lip 151 and the axial lip 152, and the height of the bent ring portion 123 from the first fitting cylindrical portion 121 in the outer diameter direction is increased. h is larger than the thickness d of the first fitting cylindrical portion 121. In addition, in the present embodiment, the bent annular portion 123 is positioned on the vehicle body side in the axis L direction from the second annular portion 142, and the outer diameter side portion of the bent annular portion 123 is the second annular portion 142. The vehicle body side surface 142c is formed so as to reach a position overlapping with the axis L direction. The radial lip 151 and the axial lip 152 in the illustrated example are formed so as to come into contact with the outer peripheral surface 4b of the inner ring member 4 and the wheel side surface 122a of the first annular ring portion 122 with elastic deformation (with a crimping margin), respectively. Each two-dot chain line shows the original shape before elastic deformation.

本実施形態において、弾性部材１５は、ゴム等のエラストマーからなり、リップ基部１５０を介して、芯金１４の所定部位に加硫成型によって一体に固着されている。具体的には、リップ基部１５０は、芯金１４における第２円輪部１４２の車輪側面１４２ａの一部から内径側端部１４２ｂを回り込み、第２円輪部１４２の車体側面１４２ｃ及び第２嵌合円筒部１４１の内周面１４１ｂの全面を覆うように芯金１４に一体に固着されている。さらに、リップ基部１５０は、第２嵌合円筒部１４１の車体側端部１４１ｃを回り込み、外輪２と第２嵌合円筒部１４１との嵌合部に至るように芯金１４に一体に固着されている。前記ラジアルリップ１５１は、リップ基部１５０から軸受空間Ｓ側（内側）に縮径するように延びるテーパ形状に形成され、前記アキシャルリップ１５２は、リップ基部１５０から軸受空間Ｓとは反対側（外側）に拡径するように延びるテーパ形状に形成されている。リップ基部１５０における外輪２と第２嵌合円筒部１４１との嵌合部に至る部分には、外輪２の内周面２ｂと第２嵌合円筒部１４１の外周面１４１ｄとの間に圧縮状態で介在する環状突部１５３が形成されている。図例では、環状突部１５３の圧縮前の原形を２点鎖線で示している。また、リップ基部１５０における第２嵌合円筒部１４１の内周面１４１ｂを覆う部分と第１円輪部１２２の外径側端部１２２ｂとの間にラビリンスｒが形成される。 In the present embodiment, the elastic member 15 is made of an elastomer such as rubber and is integrally fixed to a predetermined portion of the core metal 14 by vulcanization molding via the lip base 150. Specifically, the lip base portion 150 wraps around the inner diameter side end portion 142b from a part of the wheel side surface 142a of the second annular portion 142 of the core metal 14, and the vehicle body side surface 142c and the second fitting of the second annular portion 142. It is integrally fixed to the cored bar 14 so as to cover the entire inner peripheral surface 141b of the combined cylindrical portion 141. Further, the lip base 150 is integrally fixed to the metal core 14 so as to go around the vehicle body side end portion 141c of the second fitting cylindrical portion 141 and reach the fitting portion between the outer ring 2 and the second fitting cylindrical portion 141. ing. The radial lip 151 is formed in a taper shape extending from the lip base 150 to the bearing space S side (inner side), and the axial lip 152 is opposite to the bearing space S from the lip base 150 (outer side). It is formed in the taper shape extended so that it may expand in diameter. A portion of the lip base 150 reaching the fitting portion between the outer ring 2 and the second fitting cylindrical portion 141 is compressed between the inner circumferential surface 2b of the outer ring 2 and the outer circumferential surface 141d of the second fitting cylindrical portion 141. An annular protrusion 153 is formed between the two. In the illustrated example, the original shape of the annular protrusion 153 before compression is indicated by a two-dot chain line. Further, a labyrinth r is formed between a portion of the lip base 150 that covers the inner peripheral surface 141 b of the second fitting cylindrical portion 141 and the outer diameter side end portion 122 b of the first annular ring portion 122.

スリンガ１２における屈曲円輪部１２３の第１嵌合円筒部１２１からの外径方向高さｈは０．６ｍｍ以上とされ、さらに、屈曲円輪部１２３の厚さｄ１は第１嵌合円筒部１２１の厚さｄより小とされている。屈曲円輪部１２３の第１嵌合円筒部１２１に対する屈曲角度αは８０°以上９５°以下（図例では略９０°）とされている。屈曲円輪部１２３と弾性部材１５との最小隙間ｃは、０．４ｍｍ以上とされている。ここに最小隙間ｃとは、屈曲円輪部１２３と弾性部材１５との隙間で最も小さい部分を指す。図例では、弾性部材１５のリップ基部１５０と屈曲円輪部１２３の車輪側面１２３ａとの隙間Ｇ１が最も小さいのでこの部分の隙間を最小隙間ｃとしている。しかし、設計上屈曲円輪部１２３の外径側端面１２３ｂとアキシャルリップ１５２の基部１５２ａとの隙間Ｇ２が最も小さくなる場合は、この部分の隙間が最小隙間ｃとされる。 The height h of the bent ring part 123 from the first fitting cylindrical part 121 in the slinger 12 is 0.6 mm or more, and the thickness d1 of the bent ring part 123 is the first fitting cylindrical part. The thickness is smaller than the thickness d of 121. The bending angle α of the bent ring portion 123 with respect to the first fitting cylindrical portion 121 is set to 80 ° or more and 95 ° or less (approximately 90 ° in the illustrated example). The minimum gap c between the bent ring portion 123 and the elastic member 15 is 0.4 mm or more. Here, the minimum gap c refers to the smallest part of the gap between the bent ring portion 123 and the elastic member 15. In the illustrated example, the gap G1 between the lip base portion 150 of the elastic member 15 and the wheel side surface 123a of the bent ring portion 123 is the smallest, so the gap in this portion is the minimum gap c. However, when the gap G2 between the outer diameter side end surface 123b of the bent ring portion 123 and the base portion 152a of the axial lip 152 is the smallest in terms of design, the gap in this portion is set to the minimum gap c.

前記のように構成されるベアリングシール（軸受密封装置）１１が装着された軸受装置１において、ドライブシャフト７が軸Ｌ回りに回転すると、内輪５（ハブ輪３及び内輪部材４）が軸Ｌ回りに一体に回転し、スリンガ１２も一体に回転する。この回転に伴い、ラジアルリップ１５１の先端部が内輪部材４の外周面４ｂに弾性的に相対摺接し、また、アキシャルリップ１５２の先端部がスリンガ１２における第１円輪部１２２の車輪側面１２２ａに弾性的に相対摺接する。前記ラビリンスｒの存在と、このラジアルリップ１５１、アキシャルリップ１５２の弾性的相対摺接とにより、ドライブシャフト７の稼働中における外部からの泥水等の軸受空間Ｓ内への浸入が阻止され、また、軸受空間Ｓ内に充填された潤滑剤の外部漏出が阻止される。 In the bearing device 1 equipped with the bearing seal (bearing sealing device) 11 configured as described above, when the drive shaft 7 rotates about the axis L, the inner ring 5 (the hub ring 3 and the inner ring member 4) rotates about the axis L. The slinger 12 also rotates integrally. Along with this rotation, the distal end portion of the radial lip 151 is elastically slidably contacted with the outer peripheral surface 4 b of the inner ring member 4, and the distal end portion of the axial lip 152 is in contact with the wheel side surface 122 a of the first annular portion 122 of the slinger 12. Relative sliding contact elastically. Due to the presence of the labyrinth r and the elastic relative sliding contact between the radial lip 151 and the axial lip 152, intrusion of muddy water from the outside into the bearing space S during operation of the drive shaft 7 is prevented, and External leakage of the lubricant filled in the bearing space S is prevented.

しかし、自動車用の軸受装置のように過酷な泥水環境下に晒される場合、前記ラビリンスｒを経てベアリングシール１１内に泥水等が浸入することがある。そして、浸入した泥水の一部がアキシャルリップ１５２の先端部と第２円輪部１２２の車輪側面１２２ａとの相対摺接部に到達し、泥水等に含まれる異物が当該相対摺接部に噛み込んで、アキシャルリップ１５２の先端部が経時的に摩耗することがる。このような摩耗が生じると、泥水等がアキシャルリップ１５２の先端部と第２円輪部１２２の車輪側面１２２ａとの相対摺接部を通過する。しかし、泥水等がアキシャルリップ１５２の先端部と第２円輪部１２２の車輪側面１２２ａとの相対摺接部を通過したとしても、泥水等は屈曲円輪部１２３によって堰き止められて、屈曲円輪部１２３、第１嵌合円筒部１２１及び第１円輪部１２２で形成される溝状空間に一時的に滞留する。この溝状空間は環状であるから、泥水等は一時的に滞留するも溝状空間内を下方に流れてアキシャルリップ１５２の前記相対摺接部を経て速やかに排出される。したがって、当該ベアリングシール１１内に泥水等が一時的に浸入しても、泥水等がラジアルリップ１５１と内輪部材４の外周面４ｂとの相対摺接部に到達することは少なく、泥水等の当該相対摺接部への噛み込みによるラジアルリップ１５１の先端部の摩耗が生じることが抑制される。しかも、屈曲円輪部１２３の第１嵌合円筒部１２１からの外径方向高さｈが第１嵌合円筒部１２１の厚さｄより大とされているから、屈曲円輪部１２３の前記堰止め機能が効果的に発揮され、当該ベアリングシール１１のシール機能が長く維持されてその長寿命化が図られる。本実施形態では、屈曲円輪部１２３の前記径方向高さｈが０．６ｍｍ以上とされているから、前記泥水等の堰止め機能がより効果的に発揮される。因みに、屈曲円輪部１２３の径方向高さｈが０．６ｍｍ未満の場合は、屈曲円輪部１２３の堰止め機能が低下する傾向となり、ラジアルリップ１５１の先端部と内輪部材４の外周面４ｂとの相対摺接部に泥水等が到達する懸念が生じ易くなる。 However, when exposed to a severe muddy water environment such as a bearing device for automobiles, muddy water or the like may enter the bearing seal 11 through the labyrinth r. Then, a part of the infiltrated muddy water reaches the relative sliding contact portion between the tip end portion of the axial lip 152 and the wheel side surface 122a of the second annular ring portion 122, and the foreign matter contained in the muddy water bites into the relative sliding contact portion. As a result, the tip of the axial lip 152 may wear over time. When such wear occurs, muddy water or the like passes through the relative sliding contact portion between the tip end portion of the axial lip 152 and the wheel side surface 122a of the second annular ring portion 122. However, even if muddy water or the like passes through the relative sliding contact portion between the tip end portion of the axial lip 152 and the wheel side surface 122a of the second annular ring portion 122, the muddy water or the like is blocked by the bent circular ring portion 123 and is bent. It stays temporarily in the groove-like space formed by the ring portion 123, the first fitting cylindrical portion 121, and the first ring portion 122. Since this groove-like space is annular, muddy water or the like stays temporarily but flows downward in the groove-like space and is quickly discharged through the relative sliding contact portion of the axial lip 152. Therefore, even if muddy water or the like temporarily enters the bearing seal 11, muddy water or the like hardly reaches the relative sliding contact portion between the radial lip 151 and the outer peripheral surface 4 b of the inner ring member 4. Abrasion of the tip end portion of the radial lip 151 due to biting into the relative sliding contact portion is suppressed. Moreover, since the outer height h of the bent ring portion 123 from the first fitting cylindrical portion 121 is greater than the thickness d of the first fitting cylindrical portion 121, The damming function is effectively exhibited, the sealing function of the bearing seal 11 is maintained for a long time, and the service life is extended. In the present embodiment, since the radial height h of the bent ring portion 123 is 0.6 mm or more, the function of blocking the muddy water or the like is more effectively exhibited. Incidentally, when the radial height h of the bent ring portion 123 is less than 0.6 mm, the damming function of the bent ring portion 123 tends to be lowered, and the distal end portion of the radial lip 151 and the outer peripheral surface of the inner ring member 4 There is a concern that muddy water or the like may reach the relative sliding contact portion with 4b.

また、本実施形態では、屈曲円輪部１２３の厚さｄ１が第１嵌合円筒部１２１の厚さｄより小とされているから、屈曲円輪部１２３の屈曲板金加工が容易になされる。通常、この種のスリンガ１２は、厚さ０．６ｍｍのステンレス鋼板を板金加工することにより作製され、屈曲円輪部１２３は第１嵌合円筒部１２１の車輪側延長部を屈曲加工することによって形成されるので、厚さｄ１が厚さｄより小さいことによりこの屈曲加工がし易くなる。また、屈曲円輪部１２３と弾性部材１５との最小隙間ｃは、０．４ｍｍ以上とされているから、不可避的なベアリングシール１１の設計公差や内輪５および外輪２の偏心等があっても、内輪５と外輪２との相対的軸回転の際に、屈曲円輪部１２３と弾性部材１５とが接触する懸念がない。なお、最小隙間ｃの上限値は、当該軸受装置１の仕様によるベアリングシール１１が装着されるスペースの制約等を勘案して定められる。 In the present embodiment, since the thickness d1 of the bent ring portion 123 is smaller than the thickness d of the first fitting cylindrical portion 121, the bent sheet metal processing of the bent ring portion 123 is facilitated. . Usually, this kind of slinger 12 is produced by sheet metal processing a stainless steel plate having a thickness of 0.6 mm, and the bent ring part 123 is formed by bending the wheel side extension of the first fitting cylindrical part 121. Since it is formed, the bending process is facilitated by the fact that the thickness d1 is smaller than the thickness d. Further, since the minimum clearance c between the bent ring portion 123 and the elastic member 15 is 0.4 mm or more, even if there is an inevitable design tolerance of the bearing seal 11 or eccentricity of the inner ring 5 and the outer ring 2. During the relative axial rotation of the inner ring 5 and the outer ring 2, there is no concern that the bent ring portion 123 and the elastic member 15 come into contact. Note that the upper limit value of the minimum clearance c is determined in consideration of the restriction of the space in which the bearing seal 11 is mounted according to the specifications of the bearing device 1.

前記のように構成されるベアリングシール１１の性能試験を実施した。
＜性能試験方法＞
図２示すように構成されるベアリングシール１１を内輪５と外輪２との間に装着した状態で、軸Ｌより下半部分を泥水浴中にディップし、この状態で内輪５を１１００ｒｐｍの速度で回転させ、回転開始から軸受空間Ｓ側に泥水が漏出し始めるまでの経過時間を計測した。泥水の漏出はセンサーにて確認した。
試験サンプルとして、比較例（高さｈ＝０ｍｍ）、実施例１（高さｈ＝０．８ｍｍ）、実施例２（高さｈ＝１．６ｍｍ）の、各２個ずつ準備し、これらの前記経過時間を計測した。
＜性能試験結果＞
図３に性能試験の結果を示す。図３において、目標の経過時間を１００とし、各計測時間を目標の経過時間に対する百分率で示している。
この性能試験の結果から、比較例では、経過時間のばらつきが大きく、目標の経過時間を下回る場合もある。これは、外部からベアリングシール１１内に浸入した泥水に含まれる異物が、アキシャルリップ１５２の先端部と第１円輪部１２２の車輪側面１２２ａとの摺接部に噛み込み、経時的にアキシャルリップ１５２の先端部が摩耗して泥水が通過してラジアルリップ１５１側に到達し、そのまま、ラジアルリップ１５１の先端部と内輪部材４の外周面４ｂとの摺接部を通過することがあるためと考えられる。これに対して、実施例１及び実施例２では、確実に目標の経過時間を上回り、しかも、高さｈが大きくなる程ばらつきが小さくなることが理解される。このことから、屈曲円輪部１２３が存在することにより、アキシャルリップ１５２の先端部と第１円輪部１２２の車輪側面１２２ａとの摺接部を通過した泥水は、屈曲円輪部１２３によって一時的に堰き止められてラジアルリップ１５１側への到達が遅延されると考えられる。そして、屈曲円輪部１２３によって一時的に堰き止められた泥水は、内輪部材４の外周面４ｂを流下してアキシャルリップ１５２の先端部と第１円輪部１２２の車輪側面１２２ａとの摺接部を再度通過してラビリンスｒを経て外部に排出される。特に、屈曲円輪部１２３の高さｈが０．６ｍｍ以上であるとこの現象が顕著であり、シール機能が長く維持される。 A performance test of the bearing seal 11 configured as described above was performed.
<Performance test method>
In a state where the bearing seal 11 configured as shown in FIG. 2 is mounted between the inner ring 5 and the outer ring 2, the lower half portion from the shaft L is dipped in a muddy water bath, and in this state, the inner ring 5 is moved at a speed of 1100 rpm. The time elapsed from the start of rotation until the muddy water started to leak out to the bearing space S side was measured. The leakage of muddy water was confirmed by a sensor.
As a test sample, a comparative example (height h = 0 mm), an example 1 (height h = 0.8 mm), and an example 2 (height h = 1.6 mm) were each prepared in two pieces. The elapsed time was measured.
<Results of performance test>
FIG. 3 shows the results of the performance test. In FIG. 3, the target elapsed time is set to 100, and each measurement time is shown as a percentage with respect to the target elapsed time.
From the results of this performance test, in the comparative example, the variation in the elapsed time is large and sometimes less than the target elapsed time. This is because foreign matter contained in the muddy water that has entered the bearing seal 11 from the outside bites into the sliding contact portion between the tip end portion of the axial lip 152 and the wheel side surface 122a of the first annular ring portion 122, and the axial lip gradually changes. Because the tip of 152 is worn and the muddy water passes and reaches the radial lip 151 side, and may pass through the sliding contact portion between the tip of the radial lip 151 and the outer peripheral surface 4b of the inner ring member 4 as it is. Conceivable. On the other hand, in Example 1 and Example 2, it is understood that the target elapsed time is surely exceeded and the variation becomes smaller as the height h becomes larger. Therefore, the presence of the bent ring portion 123 causes the muddy water that has passed through the sliding contact portion between the tip portion of the axial lip 152 and the wheel side surface 122a of the first ring portion 122 to be temporarily transmitted by the bent ring portion 123. It is considered that the arrival to the radial lip 151 side is delayed due to the damming. Then, the muddy water temporarily blocked by the bent ring portion 123 flows down the outer peripheral surface 4 b of the inner ring member 4 and slides between the tip of the axial lip 152 and the wheel side surface 122 a of the first annular portion 122. It passes through the part again and is discharged to the outside through the labyrinth r. In particular, when the height h of the bent ring portion 123 is 0.6 mm or more, this phenomenon is remarkable, and the sealing function is maintained for a long time.

図４は、本発明に係る軸受密封装置の別の実施形態を示す。本実施形態のベアリングシール（軸受密封装置）１１においては、屈曲円輪部１２３は、その外径側端面１２３ｂが、第２円輪部１４２の内径側端部１４２ｂに径方向に対向するように形成されている。そして、本実施形態では、屈曲円輪部１２３の外径側端面１２３ｂとリップ基部１５０における第２円輪部１４２の内径側端部１４２ｂを回り込む部分との間に、屈曲円輪部１２３と弾性部材１５との隙間Ｇ３が最小隙間ｃとされている。この最小隙間ｃは、前記例と同様に０．４ｍｍ以上とされる。したがって、不可避的なベアリングシール１１の設計公差や内輪５および外輪２の偏心等があっても、内輪５と外輪２との相対的軸回転の際に、屈曲円輪部１２３と弾性部材１５とが接触する懸念がない。この場合も、屈曲円輪部１２３の第１嵌合円筒部１２１からの外径方向高さｈは、図２に示す実施形態の外径方向高さｈより小さいが、第１嵌合円筒部１２１の厚さｄより大とされる。これにより、屈曲円輪部１２３の堰止め機能が前記と同様に効果的に発揮される。
なお、その他の寸法関係を含むその他の構成は、図２に示す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、その構成及び作用効果の説明を割愛する。 FIG. 4 shows another embodiment of the bearing sealing device according to the present invention. In the bearing seal (bearing sealing device) 11 of the present embodiment, the bent annular portion 123 has an outer diameter side end surface 123b opposed to the inner diameter side end portion 142b of the second annular portion 142 in the radial direction. Is formed. In the present embodiment, the bending ring portion 123 and the elastic portion between the outer diameter side end surface 123b of the bending ring portion 123 and the portion of the lip base 150 that wraps around the inner diameter side end portion 142b of the second annular portion 142 are elastic. The gap G3 with the member 15 is the minimum gap c. The minimum gap c is set to 0.4 mm or more as in the above example. Therefore, even if there is an inevitable design tolerance of the bearing seal 11 and the eccentricity of the inner ring 5 and the outer ring 2, the bent ring portion 123 and the elastic member 15 There is no concern of contact. Also in this case, the outer diameter direction height h from the first fitting cylindrical part 121 of the bent ring part 123 is smaller than the outer diameter direction height h of the embodiment shown in FIG. The thickness is set to be greater than 121. Thereby, the damming function of the bent ring portion 123 is effectively exhibited as described above.
Since other configurations including other dimensional relationships are the same as those in the embodiment shown in FIG. 2, the same reference numerals are given to common portions, and descriptions of the configurations and functions and effects are omitted.

図５は、本発明に係る軸受密封装置のさらに別の実施形態を示す。本実施形態のベアリングシール（軸受密封装置）１１は、スリンガ（金属環）１２が、第１円輪部１２２の外径側端部１２２ｂから軸Ｌ方向内側（車輪側）に延びる円筒部１２４をさらに備えている点で図２に示す実施形態と異なる。加えて、弾性部材１５は、スリンガ１２における屈曲円輪部１２３の車輪側面１２３ａに弾性的に接触する第２のアキシャルリップ１５４を有している。そして、円筒部１２４の外周面１２４ａと、リップ基部１５０における第２嵌合円筒部１４１の内周面１４１ｂを覆う部分との間には前記実施形態より長いラビリンスｒ１が形成されている。本実施形態でも、屈曲円輪部１２３の第１嵌合円筒部１２１からの外径方向高さｈが第１嵌合円筒部１２１の厚さｄより大とされる。その他の寸法関係も、前記実施形態と同様に設定される。 FIG. 5 shows still another embodiment of the bearing sealing device according to the present invention. The bearing seal (bearing sealing device) 11 of this embodiment includes a cylindrical portion 124 in which a slinger (metal ring) 12 extends inward in the axis L direction (wheel side) from the outer diameter side end portion 122b of the first annular ring portion 122. Furthermore, it differs from the embodiment shown in FIG. In addition, the elastic member 15 has a second axial lip 154 that elastically contacts the wheel side surface 123 a of the bent ring portion 123 of the slinger 12. A labyrinth r1 longer than that of the above embodiment is formed between the outer peripheral surface 124a of the cylindrical portion 124 and the portion of the lip base 150 that covers the inner peripheral surface 141b of the second fitting cylindrical portion 141. Also in this embodiment, the height h in the outer diameter direction of the bent ring portion 123 from the first fitting cylindrical portion 121 is made larger than the thickness d of the first fitting cylindrical portion 121. Other dimensional relationships are set in the same manner as in the above embodiment.

本実施形態のベアリングシール１１においては、スリンガ１２が円筒部１２４を有していることにより、前記実施形態のラビリンスｒより長いラビリンスｒ１が形成される。これにより、泥水等のベアリングシール１１内への浸入経路が長くなり、外部からのベアリングシール１１内への泥水等の浸入がより生じ難くなる。仮に、ラビリンスｒ１を経てベアリングシール１１内に泥水等が浸入しても、スリンガ１２の回転に伴う円筒部１２４とアキシャルリップ１５２とで形成される空間部におけるポンピング作用によって泥水等がラビリンスｒ１を経て外部に速やかに排出される。したがって、アキシャルリップ１５２の先端部と第１円輪部１２２の車輪側面１２２ａとの弾性的な相対摺接部に泥水等に含まれる異物が噛み込むことが少なく、アキシャルリップ１５２の先端部の摩耗促進が抑えられる。さらに、第２のアキシャルリップ１５４が屈曲円輪部１２３の車輪側面１２３ａに弾性的に相対摺接するから、屈曲円輪部１２３の堰止め効果とアキシャルリップ１５４のシール機能とが相乗して、ラジアルリップ１５１と内輪部材４との弾性的な相対摺接部への泥水の到達がより効果的に遅延される。これによりベアリングシール１１がより長寿命化される。
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 bearing seal 11 of this embodiment, the labyrinth r1 longer than the labyrinth r of the above embodiment is formed by the slinger 12 having the cylindrical portion 124. As a result, the infiltration path of muddy water or the like into the bearing seal 11 becomes longer, and entry of muddy water or the like into the bearing seal 11 from the outside is less likely to occur. Even if muddy water or the like enters the bearing seal 11 through the labyrinth r1, the muddy water or the like passes through the labyrinth r1 due to the pumping action in the space formed by the cylindrical portion 124 and the axial lip 152 as the slinger 12 rotates. It is quickly discharged to the outside. Therefore, foreign matter contained in muddy water or the like is less likely to be caught in the elastic relative sliding contact portion between the tip portion of the axial lip 152 and the wheel side surface 122a of the first annular ring portion 122, and the tip portion of the axial lip 152 is worn. Promotion is suppressed. Furthermore, since the second axial lip 154 is elastically slidably contacted with the wheel side surface 123a of the bent ring portion 123, the weiring effect of the bent ring portion 123 and the sealing function of the axial lip 154 are synergistic, and the radial The arrival of muddy water at the elastic relative sliding contact portion between the lip 151 and the inner ring member 4 is more effectively delayed. Thereby, the life of the bearing seal 11 is further extended.
Since other configurations are the same as those of the above-described embodiment, common portions are denoted by the same reference numerals, and description thereof is omitted.

図６は、図５に示す例の変形例を示す。本例のベアリングシール（軸受密封装置）１１においては、シール部材１３の弾性部材１５が、図５に示す例の第２のアキシャルリップ１５４に代え、アキシャルリップ１５２の外径側に、環状の鉤型突部１５５を一体に有している。この鉤型突部１５５は、断面形状が、前記と同様のリップ基部１５０における芯金１４の車体側面１４２ｃを覆う部分からスリンガ（金属環）１２の第１円輪部１２２側（車体側）に円筒状に延び、且つ、その先端部からスリンガ１２の円筒部１２４側（外径側）に屈曲するよう延びる鉤型の形状とされている。また、屈曲円輪部１２３は、図２に示す実施形態と同様に、第２円輪部１４２より軸Ｌ方向の車体側に位置し、且つ、屈曲円輪部１２３の外径側部分が第２円輪部１４２の車体側面１４２ｃに軸Ｌ方向に重なる位置に及ぶように形成されている。そして、弾性部材１５のリップ基部１５０と屈曲円輪部１２３の車輪側面１２３ａとの隙間が最小隙間ｃとされている。しかし、前記と同様に、設計上屈曲円輪部１２３の外径側端面１２３ｂとアキシャルリップ１５２の基部１５２ａとの隙間が最も小さくなる場合は、この部分の隙間が最小隙間ｃとされる。 FIG. 6 shows a modification of the example shown in FIG. In the bearing seal (bearing sealing device) 11 of the present example, the elastic member 15 of the seal member 13 replaces the second axial lip 154 of the example shown in FIG. The mold protrusion 155 is integrally formed. The saddle-shaped protrusion 155 has a cross-sectional shape from the portion covering the vehicle body side surface 142c of the core metal 14 in the lip base 150 similar to the above to the first ring portion 122 side (vehicle body side) of the slinger (metal ring) 12. It has a bowl-like shape extending in a cylindrical shape and extending from its distal end portion so as to bend toward the cylindrical portion 124 side (outer diameter side) of the slinger 12. Further, similarly to the embodiment shown in FIG. 2, the bent annular portion 123 is located on the vehicle body side in the axis L direction from the second annular portion 142, and the outer diameter side portion of the bent annular portion 123 is the first one. It is formed so as to reach a position overlapping the vehicle body side surface 142c of the two-ring portion 142 in the axis L direction. The gap between the lip base 150 of the elastic member 15 and the wheel side surface 123a of the bent ring portion 123 is the minimum gap c. However, in the same manner as described above, when the gap between the outer diameter side end surface 123b of the bent circular ring portion 123 and the base portion 152a of the axial lip 152 is the smallest in design, the gap in this portion is set as the minimum gap c.

本例のベアリングシール１１においては、スリンガ１２の円筒部１２４とアキシャルリップ１５２との間に鉤型突部１５５が存在するから、スリンガ１２の回転に伴う円筒部１２４とアキシャルリップ１５２とで形成される空間部におけるポンピング作用がより活発化する。これによって、ラビリンスｒ１を経てベアリングシール１１内に泥水等が浸入しても、泥水等がラビリンスｒ１を経て外部に速やかに排出される。また、鉤型突部１５５はリップ基部１５０とともに環状の溝形状をなすから、浸入した泥水等の一部は、鉤型突部１５５による溝形状部分を下方に流れてラビリンスｒ１を経て外部に排出される。したがって、アキシャルリップ１５２の先端部と第１円輪部１２２の車輪側面１２２ａとの弾性的な相対摺接部に泥水等が到達し難く、泥水等に含まれる異物がこの相対摺接部に噛み込むことがより少なくなり、アキシャルリップ１５２の先端部の摩耗促進が抑えられる。この鉤型突部１５５の機能と、屈曲円輪部１２３の堰止め効果とが相乗して、回転トルクが増大することなく、ラジアルリップ１５１と内輪部材４との弾性的な相対摺接部への泥水の到達がより効果的に遅延される。これによりベアリングシール１１がより長寿命化される。
なお、本例において、環状の鉤型突部１５５に代えて、リップ基部１５０からスリンガ１２の円筒部１２４に向け車体側に拡径して延びるテーパ状突部を設けても良い。その他の構成は図５に示す例と同様であるから、共通部分に同一の符号を付し、その説明を割愛する。 In the bearing seal 11 of this example, since the saddle-shaped protrusion 155 exists between the cylindrical portion 124 of the slinger 12 and the axial lip 152, the cylindrical seal 124 and the axial lip 152 are formed as the slinger 12 rotates. The pumping action in the space is more active. Accordingly, even if muddy water or the like enters the bearing seal 11 via the labyrinth r1, the muddy water or the like is quickly discharged to the outside via the labyrinth r1. Further, since the saddle-shaped protrusion 155 forms an annular groove shape together with the lip base 150, a part of the infiltrated muddy water or the like flows down the groove-shaped part of the saddle-shaped protrusion 155 and is discharged to the outside through the labyrinth r1. Is done. Accordingly, muddy water or the like hardly reaches the elastic relative sliding contact portion between the tip end portion of the axial lip 152 and the wheel side surface 122a of the first annular ring portion 122, and foreign matter contained in the muddy water bites into the relative sliding contact portion. The wear of the front end portion of the axial lip 152 is suppressed. The function of the saddle-shaped protrusion 155 and the weiring effect of the bent annular portion 123 are synergistic, and the elastic relative sliding contact portion between the radial lip 151 and the inner ring member 4 is increased without increasing the rotational torque. The arrival of mud is delayed more effectively. Thereby, the life of the bearing seal 11 is further extended.
In this example, instead of the annular saddle-shaped protrusion 155, a tapered protrusion that extends from the lip base 150 toward the cylindrical portion 124 of the slinger 12 toward the vehicle body side may be provided. Since the other configuration is the same as the example shown in FIG. 5, the same reference numerals are given to the common parts, and the description thereof is omitted.

なお、各実施形態では、ラジアルリップ１５１およびアキシャルリップ１５２は、それぞれ内輪部材４の外周面４ｂ及び第１円輪部１２２の車体側面１２２ａに弾性的に接触しているが、これらはいずれも各対象面に対して単に接触しているものであってもよい。また、各実施形態では、外輪（外径側部材）２が固定側、内輪（内径側部材）５が回転側としたが、これに限らず、外輪２が回転側、内輪５が固定側であってもよい。さらに、本発明の軸受密封装置を図１の車体側のベアリングシール１１に適用した例について述べたが、車輪側のベアリングシール１０に適用することも可能である。また、適用される軸受装置をハブベアリングとしたが、その他のタイプの軸受装置であってもよい。加えて、本発明に係る軸受密封装置は、自動車用の軸受装置に適用される例について述べたが、これに限らず、相対的に同軸回転する外径側部材と内径側部材との間の環状空間に装着される軸受密封装置であれば、他の産業分野の軸受装置にも好ましく適用される。また、自動車用の軸受装置であっても、駆動輪用に限らず従動輪用の軸受装置であってよい。さらにまた、スリンガ１２及びシール部材１３の形状やシールリップの数等も要求される仕様等に応じて適宜変更が可能である。 In each embodiment, the radial lip 151 and the axial lip 152 are in elastic contact with the outer peripheral surface 4b of the inner ring member 4 and the vehicle body side surface 122a of the first annular ring portion 122, respectively. It may be simply in contact with the target surface. In each embodiment, the outer ring (outer diameter side member) 2 is the fixed side, and the inner ring (inner diameter side member) 5 is the rotation side. However, the outer ring 2 is the rotation side and the inner ring 5 is the fixed side. There may be. Furthermore, although the example which applied the bearing sealing apparatus of this invention to the bearing seal 11 by the side of the vehicle body of FIG. 1 was described, it is also possible to apply to the bearing seal 10 by the side of a wheel. Moreover, although the applied bearing device is a hub bearing, other types of bearing devices may be used. In addition, the bearing sealing device according to the present invention has been described with respect to an example applied to a bearing device for an automobile. Any bearing sealing device mounted in an annular space is preferably applied to bearing devices in other industrial fields. Moreover, even if it is a bearing apparatus for motor vehicles, it may be a bearing apparatus for driven wheels, not only for driving wheels. Furthermore, the shape of the slinger 12 and the seal member 13, the number of seal lips, and the like can be appropriately changed according to the required specifications.

１軸受装置
２外輪（外径側部材）
２ｂ内周面
３ハブ輪（内輪）
４内輪部材（内輪）
４ｂ外周面
５内輪（内径側部材）
１０，１１ベアリングシール（軸受密封装置）
１２スリンガ（金属環）
１２１第１嵌合円筒部
１２１ａ車体側端部（軸方向外側端部）
１２２第１円輪部
１２２ａ外径側端部
１２３屈曲円輪部
１２４円筒部
１３シール部材
１４芯金
１４１第２嵌合円筒部
１４１ａ車輪側端部（軸方向内側端部）
１４２第２円輪部
１５弾性部材
１５１ラジアルリップ
１５２アキシャルリップ
ｈ屈曲円輪部の第１嵌合円筒部からの外径方向高さ
ｄ第１嵌合円筒部の厚さ
ｄ１屈曲円輪部の厚さ
ｃ屈曲円輪部と弾性部材との最小隙間
α 屈曲円輪部の第１嵌合円筒部に対する角度 1 Bearing device 2 Outer ring (outer diameter side member)
2b Inner peripheral surface 3 Hub wheel (inner ring)
4 Inner ring member (inner ring)
4b Outer peripheral surface 5 Inner ring (inner diameter side member)
10,11 Bearing seal (bearing sealing device)
12 Slinger (metal ring)
121 1st fitting cylindrical part 121a Car body side edge part (Axial direction outer edge part)
122 1st ring part 122a Outer diameter side end part 123 Bent ring part 124 Cylindrical part 13 Seal member 14 Core metal 141 Second fitting cylindrical part 141a Wheel side end part (axially inner end part)
142 Second annular portion 15 Elastic member 151 Radial lip 152 Axial lip h Height of the bent annular portion in the outer radial direction from the first fitting cylindrical portion d Thickness of the first fitting cylindrical portion d1 of the bent annular portion Thickness c Minimum clearance between the bent ring portion and the elastic member α Angle of the bent ring portion with respect to the first fitting cylindrical portion

Claims

A bearing sealing device for sealing an annular space between an inner diameter side member and an outer diameter side member that rotate relatively coaxially,
A metal ring fitted to the inner diameter side member and a seal member fitted to the outer diameter side member are combined,
The metal ring includes a first fitting cylindrical portion that is fitted to the outer peripheral surface of the inner diameter side member, and a first annular portion that extends outward from the axially outer end portion of the first fitting cylindrical portion. A bent ring part bent from the axially inner end of the first fitting cylindrical part to the outer diameter side, and
The seal member includes a second fitting cylindrical portion fitted to the inner peripheral surface of the outer diameter side member, and a second annular portion extending from the axially inner end of the second fitting cylindrical portion toward the inner diameter side. A core metal having a radial lip that contacts the inner diameter side member and an axial lip that contacts the first circular ring portion, and an elastic member fixed to the core metal;
The bent annular portion is located between the radial lip and the axial lip, and the height of the bent annular portion from the first fitting cylindrical portion in the outer diameter direction is the first fitting cylindrical portion. A bearing sealing device characterized by being larger than the thickness.

The bearing sealing device according to claim 1,
The metal ring further includes a cylindrical portion extending inward in the axial direction from an outer diameter side end portion of the first annular portion.

The bearing sealing device according to claim 1 or 2,
The bearing sealing device according to claim 1, wherein the height of the bent ring portion in the metal ring is 0.6 mm or more.

In the bearing sealing device according to any one of claims 1 to 3,
The bearing sealing device according to claim 1, wherein a thickness of the bent ring portion in the metal ring is smaller than a thickness of the first fitting cylindrical portion.

In the bearing sealing device according to any one of claims 1 to 4,
The bearing sealing device, wherein a bending angle of the bent ring portion of the metal ring with respect to the first fitting cylindrical portion is 80 ° or more and 95 ° or less.

In the bearing sealing device according to any one of claims 1 to 5,
A bearing sealing device, wherein a minimum gap between the bent ring portion and the elastic member in the metal ring is 0.4 mm or more.