JP2005090526A - Sealing device - Google Patents

Sealing device Download PDF

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Publication number
JP2005090526A
JP2005090526A JP2003320656A JP2003320656A JP2005090526A JP 2005090526 A JP2005090526 A JP 2005090526A JP 2003320656 A JP2003320656 A JP 2003320656A JP 2003320656 A JP2003320656 A JP 2003320656A JP 2005090526 A JP2005090526 A JP 2005090526A
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Japan
Prior art keywords
side lip
sealing device
tip
lip
angle
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JP2003320656A
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Japanese (ja)
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JP4240217B2 (en
Inventor
Takeshi Kanzaki
剛 神前
Kazunori Takeno
一記 武野
Koichi Mizunoya
弘一 水野谷
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Nok Corp
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Nok Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • 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
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring
    • F16C33/7883—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sealing device 1 capable of correctly maintaining stress distribution of a side lip 6 under bad conditions such as change of interference and generation of face deflection, and thus achieving stable sealing performance. <P>SOLUTION: This sealing device 1 comprises the side lip 6 tightly applied to an axial direction end face part 5a or a curvature part of a counter member 4 to be slidable. A sliding part tip angle θ<SB>3</SB>of the side lip 6 is set as a larger angle than 90° to set the volume of the tip of the side lip 6 larger, so that the side lip 6 is less likely to be deformed. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、密封装置に係り、更に詳しくは、サイドリップを有する密封装置に関するものである。本発明の密封装置は例えばハブベアリングシールとして自動車関連分野に用いられ、または汎用機械等に用いられる。   The present invention relates to a sealing device, and more particularly to a sealing device having a side lip. The sealing device of the present invention is used, for example, in the field of automobiles as a hub bearing seal, or used for general-purpose machines.

従来から、図４に示すように、摺動の相手部材である回転ハブ６１の軸方向端面部６２または曲面部６３に摺動自在に密接するサイドリップ５２，５３を有する密封装置５１が知られており（特許文献１参照）、この密封装置５１は、ハブ６１に対するサイドリップ５２，５３のしめしろの大きさが通常状態（ＭＩＤ状態、設計狙い値）にあるときには、適正な応力分布（リップ接触圧力分布）を示し、よって安定した密封性能を発揮するように構成されている。   Conventionally, as shown in FIG. 4, a sealing device 51 having side lips 52 and 53 slidably in close contact with an axial end surface portion 62 or a curved surface portion 63 of a rotating hub 61 which is a sliding counterpart member is known. (See Patent Document 1), this sealing device 51 has an appropriate stress distribution (lip) when the size of the interference between the side lips 52 and 53 with respect to the hub 61 is in a normal state (MID state, design target value). Contact pressure distribution), and thus is configured to exhibit stable sealing performance.

しかしながら、この従来の密封装置５１によると、図５（Ａ）に拡大して示すように、サイドリップ５２の先端面５２ａが同サイドリップ５２の内周面５２ｂに対して直角に交差するように形成されていて両面５２ａ，５２ｂのなす摺動部先端頂角θ１の大きさがちょうど９０度（θ１＝９０°）に形成されているか、あるいは図５（Ｂ）に拡大して示すように、サイドリップ５３の先端面５３ａが断面Ｖ字形に形成されていて摺動部先端頂角θ２の大きさが９０度よりも小さな角度（θ２＜９０°）に形成されているために、以下のような不都合がある。 However, according to this conventional sealing device 51, as shown in an enlarged view in FIG. 5A, the front end surface 52a of the side lip 52 intersects the inner peripheral surface 52b of the side lip 52 at a right angle. The sliding portion tip apex angle θ 1 formed by both surfaces 52a and 52b is formed to be exactly 90 degrees (θ 1 = 90 °), or as shown in an enlarged view in FIG. In addition, since the front end surface 53a of the side lip 53 is formed in a V-shaped cross section, the sliding portion front end apex angle θ 2 is formed at an angle smaller than 90 degrees (θ 2 <90 °). There are the following inconveniences.

すなわち、ハブ６１がサイドリップ５２，５３に対して相対に軸方向変位すると、ハブ６１に対するサイドリップ５２，５３のしめしろの大きさが適宜変化するが、このようにサイドリップ５２，５３のしめしろの大きさが変化したり、あるいはハブ６１がサイドリップ５２，５３に対して面振れしたりすると、上記従来の密封装置５１では、上記形状によりサイドリップ５２，５３先端のボリュームが余り大きくないために、サイドリップ５２，５３の形状変化や応力変化が大きく、リップ接触状態が不安定なものとなり、特にしめしろＭＡＸ近傍では、サイドリップ５２，５３がべた当たりとなって、接触圧力ピーク値が小さくなる（しめしろＭＡＸ＋面振れＭＡＸ状態により、より厳しいべた当たりとなる）。したがって、この状態で更にラジアル方向の動き（軸偏心等）が加わると、サイドリップ５２，５３はもはや水膜を切ることができなくなり、よって密封性能が極端に低下してしまう。   That is, when the hub 61 is axially displaced relative to the side lips 52 and 53, the interference between the side lips 52 and 53 with respect to the hub 61 changes appropriately. When the size of the margin changes or the hub 61 is swung with respect to the side lips 52, 53, the volume of the tip of the side lips 52, 53 is not so large due to the above shape in the conventional sealing device 51. For this reason, the shape change and stress change of the side lips 52 and 53 are large, and the lip contact state becomes unstable. Especially in the vicinity of the interference MAX, the side lips 52 and 53 become sticky and the contact pressure peak value is reached. (Smaller stickiness due to interference MAX + runout MAX state). Accordingly, when further radial movement (axial eccentricity, etc.) is applied in this state, the side lips 52 and 53 can no longer cut the water film, and the sealing performance is extremely lowered.

特開平９−２８７６１９号公報JP-A-9-287619

本発明は以上の点に鑑みて、上記しめしろの変化や面振れの発生等の悪条件下においてもサイドリップの応力分布を適正に保つことができ、もって安定した密封性能を発揮することが可能な密封装置を提供することを目的とする。   In view of the above points, the present invention can appropriately maintain the stress distribution of the side lip even under adverse conditions such as changes in the interference and occurrence of surface runout, thereby exhibiting stable sealing performance. The object is to provide a possible sealing device.

上記目的を達成するため、本発明の請求項１による密封装置は、相手部材の軸方向端面部または曲面部に摺動自在に密接するサイドリップを有する密封装置において、前記サイドリップの摺動部先端頂角の大きさを９０度よりも大きな角度に設定したことを特徴とするものである。   In order to achieve the above object, a sealing device according to claim 1 of the present invention is a sealing device having a side lip slidably in close contact with an axial end surface portion or a curved surface portion of a mating member. The tip apex angle is set to an angle larger than 90 degrees.

また、本発明の請求項２による密封装置は、相手部材の軸方向端面部または曲面部に摺動自在に密接するサイドリップを有する密封装置において、前記サイドリップの摺動部先端頂角の大きさを９０度よりも大きくかつ１１０度以下の角度に設定したことを特徴とするものである。   According to a second aspect of the present invention, there is provided a sealing device having a side lip that is slidably brought into close contact with an axial end surface portion or curved surface portion of a mating member. This is characterized in that the angle is set to an angle greater than 90 degrees and 110 degrees or less.

サイドリップ断面形状における長さや幅等の寸法がほぼ同じでリップ材質も同じである場合、本発明の請求項１による密封装置のように、サイドリップの摺動部先端頂角の大きさを９０度よりも大きな角度に設定すると、サイドリップ先端のボリュームが従来よりも増大せしめられることになる。したがって、サイドリップが変形しにくいものとなり、サイドリップの接触状態が安定したものとなる。   When the dimensions such as length and width in the side lip cross-sectional shape are substantially the same and the lip material is also the same, as in the sealing device according to claim 1 of the present invention, the tip apex angle of the sliding portion of the side lip is set to 90. When the angle is set larger than the degree, the volume of the side lip tip is increased as compared with the conventional case. Therefore, the side lip is hardly deformed, and the contact state of the side lip is stabilized.

尚、このように本発明では、サイドリップが変形しにくくなるようサイドリップ先端のボリュームを増大させる趣旨でサイドリップの摺動部先端頂角を９０度より大きな角度（鈍角）に設定することにしたが、角度を大きくし過ぎると、サイドリップの摺動部先端に極端な応力集中が発生することがある。そこで、これを併せて対策するには、請求項２に記載したように、サイドリップの摺動部先端頂角を９０度よりも大きくかつ１１０度以下の角度（鈍角最小範囲）に設定するのが好適である。   In this way, in the present invention, in order to increase the volume of the tip of the side lip so that the side lip is difficult to deform, the tip apex angle of the sliding part of the side lip is set to an angle larger than 90 degrees (obtuse angle). However, if the angle is too large, extreme stress concentration may occur at the tip of the sliding portion of the side lip. Therefore, in order to take countermeasures together, as described in claim 2, the top vertex angle of the sliding portion of the side lip is set to an angle larger than 90 degrees and 110 degrees or less (minimum obtuse angle range). Is preferred.

本発明は、以下の効果を奏する。   The present invention has the following effects.

すなわち、上記構成を備えた本発明の請求項１による密封装置においては、サイドリップの摺動部先端頂角の大きさを９０度よりも大きな角度に設定したために、サイドリップ先端のボリュームが従来よりも増大せしめられる。したがって、サイドリップが変形しにくく、その接触状態が安定したものとなるために、しめしろの変化や面振れの発生等の悪条件下においてもサイドリップの応力分布を適正に保つことができる。したがって、サイドリップの接触面圧ピーク値が極端に小さくなって密封性能が極端に低下するのを防止することができ、これにより密封性能を安定化させることができる。また、サイドリップ先端の接触状態が安定すれば、サイドリップ先端の浮き上がりが防止されるために、この点からも密封性能を安定化させることができる。   That is, in the sealing device according to the first aspect of the present invention having the above-described configuration, the volume of the tip of the side lip is conventionally increased because the size of the apex angle of the tip of the sliding portion of the side lip is set larger than 90 degrees. It is increased more than. Therefore, the side lip is difficult to be deformed and the contact state is stabilized, so that the stress distribution of the side lip can be properly maintained even under adverse conditions such as changes in interference and occurrence of surface runout. Therefore, it can be prevented that the peak value of the contact surface pressure of the side lip becomes extremely small and the sealing performance is extremely lowered, and thus the sealing performance can be stabilized. Further, if the contact state of the side lip tip is stabilized, the side lip tip is prevented from being lifted, so that the sealing performance can be stabilized from this point.

またこれに加えて、本発明の請求項２による密封装置においては、サイドリップの摺動部先端頂角が余り大きくなり過ぎないようにこの頂角の大きさを１１０度以下の角度に設定したために、サイドリップの摺動部先端に極端な応力集中が発生するのを防止することができる。したがって、サイドリップ延いては当該密封装置の耐久性を維持・向上させることができる。   In addition, in the sealing device according to claim 2 of the present invention, the apex angle is set to an angle of 110 degrees or less so that the tip apex angle of the sliding portion of the side lip is not too large. In addition, extreme stress concentration can be prevented from occurring at the tip of the sliding portion of the side lip. Therefore, it is possible to maintain and improve the durability of the sealing device by extending the side lip.

サイドリップの摺動部先端頂角の大きさを９０度よりも大きな角度（請求項１）または９０度よりも大きくかつ１１０度以下の角度（請求項２）に設定するには、サイドリップの先端面を内周面に対して斜め（鈍角）に交差するように形成するのが好適であるが、このほか、サイドリップの先端面を断面凸状（例えば断面三角形または断面円弧形）等に形成するようにしても良い。また、サイドリップの摺動部先端には適宜、アール（断面円弧状の丸み）を付けるようにしても良い。   To set the apex angle of the sliding portion tip of the side lip to an angle larger than 90 degrees (Claim 1) or an angle larger than 90 degrees and 110 degrees or less (Claim 2), The tip surface is preferably formed so as to intersect obliquely (obtuse angle) with respect to the inner peripheral surface, but the tip surface of the side lip has a convex cross section (for example, a triangular cross section or a circular arc shape), etc. You may make it form in. Moreover, you may make it attach | subject a round (arc-shaped roundness of a cross section) suitably to the sliding part front-end | tip of a side lip.

つぎに本発明の実施例を図面にしたがって説明する。   Next, embodiments of the present invention will be described with reference to the drawings.

第一実施例・・・
図１は、本発明の第一実施例に係る密封装置１の要部断面を示している。この密封装置１は例えば自動車用車輪懸架装置におけるベアリング部にハブベアリング用シールとして用いられるものであって、以下のように構成されている。 First embodiment ...
FIG. 1 shows a cross section of a main part of a sealing device 1 according to a first embodiment of the present invention. The sealing device 1 is used, for example, as a seal for a hub bearing in a bearing portion in a vehicle wheel suspension device, and is configured as follows.

すなわち先ず、上記ベアリング部における密封装置取付部材であるベアリング外輪（図示せず）の内周側に嵌着される金属等剛材製の取付環２が設けられており、この取付環２にゴム状弾性材製の弾性体３が加硫接着されており、この弾性体３に複数のシールリップが一体成形されており、この複数のシールリップが、上記ベアリング部における相対回転部材であるハブ（図示せず）の外周側に嵌着される金属等剛材製のスリンガー４のフランジ部（径方向部）５の軸方向端面部５ａに摺動自在に密接するサイドリップ６と、スリンガー４の筒部（軸方向部）７の周面部（外周面）７ａに摺動自在に密接するダストリップ８とによって構成されている。   That is, first, a mounting ring 2 made of a rigid material such as a metal is provided on the inner peripheral side of a bearing outer ring (not shown) which is a sealing device mounting member in the bearing portion. An elastic body 3 made of a cylindrical elastic material is vulcanized and bonded, and a plurality of seal lips are integrally formed on the elastic body 3, and the plurality of seal lips are hubs (relative rotating members in the bearing portion). A side lip 6 that is slidably in close contact with an axial end surface portion 5a of a flange portion (radial direction portion) 5 of a slinger 4 made of a rigid material such as a metal that is fitted to the outer peripheral side of the slinger 4; The dust strip 8 is slidably in close contact with the peripheral surface portion (outer peripheral surface) 7a of the cylindrical portion (axial portion) 7.

上記サイドリップ６およびダストリップ８はそれぞれ、ベアリング外部の泥水やダスト等の異物がベアリング内部へ侵入しないようにこれをシールするものであって、その機能からして外向き構造とされ、特にサイドリップ６はその基端から先端へかけて径寸法が徐々に拡大するように形成されている。   Each of the side lip 6 and the dust lip 8 seals foreign matter such as muddy water and dust outside the bearing from entering the inside of the bearing, and has an outward structure because of its function. The lip 6 is formed so that its diameter gradually increases from the base end to the tip end.

また、このサイドリップ６は、その先端面６ａが内周面６ｂに対して斜め（鈍角）に交差する断面直線状に形成されており、これによりサイドリップ６は、その摺動部先端頂角θ３の大きさが９０度よりも大きくかつ１１０度以下の角度（９０°＜θ３≦１１０°、例えば約１００°）に形成されている。摺動部先端頂角θ３は、サイドリップ６の断面形状において、サイドリップ６の先端面６ａと内周面６ｂとがなす角度である。 Further, the side lip 6 is formed in a straight cross-sectional shape in which the front end surface 6a intersects obliquely (obtuse angle) with respect to the inner peripheral surface 6b, whereby the side lip 6 has a sliding portion front end apex angle. the size of the theta 3 is formed in greater than 90 degrees and 110 degrees from (90 ° <θ 3 ≦ 110 °, for example approximately 100 °). The sliding portion tip apex angle θ 3 is an angle formed by the tip surface 6 a of the side lip 6 and the inner peripheral surface 6 b in the cross-sectional shape of the side lip 6.

上記構成を備えた密封装置１を実機に装着すると、スリンガー４がサイドリップ６に対して相対に軸方向変位してスリンガー４に対するサイドリップ６のしめしろの大きさが変化したり、スリンガー４がサイドリップ６に対して相対に径方向（軸直角方向）変位して軸偏心が発生したり、スリンガー４がサイドリップ６に対して相対に揺動変位していわゆる面振れが発生したり、あるいはこれらが複合して発生したりするが、上記密封装置１は上記構成により以下の作用効果を奏する点に特徴を有している。   When the sealing device 1 having the above configuration is mounted on an actual machine, the slinger 4 is axially displaced relative to the side lip 6 to change the size of the interference of the side lip 6 with respect to the slinger 4, or the slinger 4 Displacement relative to the side lip 6 in the radial direction (perpendicular to the axis) causes shaft eccentricity, or the slinger 4 swings and displaces relative to the side lip 6 to generate so-called surface runout, or Although these may occur in combination, the sealing device 1 is characterized in that it has the following effects by the above configuration.

すなわち、上記構成の密封装置１においては、サイドリップ６の摺動部先端頂角θ３が９０度よりも大きな角度に形成されているために、サイドリップ６先端のボリュームが従来よりも実質的に増大せしめられている。これは、摺動部先端頂角が９０度以下の場合と比較して、サイドリップ６の先端面６ａがサイドリップ６の先端方向（長手方向）に突出した形状に形成されているからである。したがって、サイドリップ６が変形しにくく、その接触状態が安定したものとされているために、しめしろの変化や面振れの発生等の悪条件下においてもサイドリップ６の応力分布を適正に保つことができる。したがって、サイドリップ６の接触面圧ピーク値が極端に小さくなって密封性能が極端に低下するのを防止することができ、これにより密封性能を安定化させることができる。また、サイドリップ６先端の接触状態が安定すれば、サイドリップ６先端の浮き上がりを防止することができるために、この点からも密封性能を安定化させることができる。 That is, in the sealing device 1 having the above-described configuration, the sliding portion tip apex angle θ 3 of the side lip 6 is formed at an angle larger than 90 degrees, so that the volume of the tip of the side lip 6 is substantially larger than before. Has been increased. This is because the tip surface 6a of the side lip 6 is formed in a shape protruding in the tip direction (longitudinal direction) of the side lip 6 as compared with the case where the tip apex angle of the sliding portion is 90 degrees or less. . Therefore, since the side lip 6 is not easily deformed and the contact state thereof is stable, the stress distribution of the side lip 6 is properly maintained even under adverse conditions such as changes in interference and occurrence of surface runout. be able to. Therefore, the contact surface pressure peak value of the side lip 6 can be prevented from becoming extremely small and the sealing performance can be prevented from being extremely lowered, whereby the sealing performance can be stabilized. Further, if the contact state of the tip of the side lip 6 is stabilized, it is possible to prevent the tip of the side lip 6 from being lifted, so that the sealing performance can be stabilized also from this point.

図２は、この作用効果を比較例と比較しながら説明するものであって、同図（Ｃ）の比較例に係る密封装置１では、サイドリップ６の先端面６ａが断面Ｖ字形に形成されていてサイドリップ６の摺動部先端頂角が９０度よりも小さな角度に形成されているために、同図（Ｄ）に示すように、スリンガー４がサイドリップ６に対して相対に近付く方向に軸方向変位すると、サイドリップ６の接触面圧ピーク値ｐが極端に小さくなる。これに対して、同図（Ａ）の当該実施例に係る密封装置１では、サイドリップ６の先端面６ａが当該サイドリップ６の長手方向に対して斜め（鈍角）に交差する断面直線状に形成されていてサイドリップ６の摺動部先端頂角が９０度より大きな角度に形成されているために、同図（Ｂ）に示すように、サイドリップ６の接触面圧ピーク値ｐが比較的大きく確保される。この両者の違いは、サイドリップ６先端のボリュームの大小に由来し、特に実施例では、同図（Ｂ）の拡大図に示すように、摺動部先端６ｃの更に外周側にリップ先端面６ａが位置して、サイドリップ６先端をスリンガー４に押し付ける向きのモーメントが作用するからであると考えられる。   FIG. 2 explains this operation and effect in comparison with a comparative example. In the sealing device 1 according to the comparative example of FIG. 2C, the front end surface 6a of the side lip 6 is formed in a V-shaped cross section. Since the tip angle of the sliding portion of the side lip 6 is smaller than 90 degrees, the direction in which the slinger 4 approaches the side lip 6 as shown in FIG. When displaced in the axial direction, the contact surface pressure peak value p of the side lip 6 becomes extremely small. On the other hand, in the sealing device 1 according to the embodiment of FIG. 5A, the front end surface 6a of the side lip 6 has a linear cross section that intersects obliquely (obtuse angle) with respect to the longitudinal direction of the side lip 6. Since the tip end angle of the sliding part of the side lip 6 is larger than 90 degrees, the contact surface pressure peak value p of the side lip 6 is compared as shown in FIG. Secure. The difference between the two results from the size of the volume at the tip of the side lip 6. In particular, in the embodiment, as shown in the enlarged view of FIG. This is considered to be because a moment in the direction of pressing the tip of the side lip 6 against the slinger 4 acts.

また、上記密封装置１においては併せて、サイドリップ６の摺動部先端頂角θ３が１１０度以下の角度に設定されているために、摺動部先端６ｃに極端な応力集中が発生するのを防止することができ、よってサイドリップ６の耐久性が低下するのを防止することができる。 Further, in the sealing device 1 as well, since the sliding portion tip apex angle θ 3 of the side lip 6 is set to an angle of 110 degrees or less, extreme stress concentration occurs at the sliding portion tip 6c. Therefore, it is possible to prevent the durability of the side lip 6 from being lowered.

第二実施例・・・
図３は、本発明の第二実施例に係る密封装置１の要部断面を示している。この密封装置１は例えば自動車用車輪懸架装置におけるベアリング部にハブベアリング用シールとして用いられるものであって、以下のように構成されている。 Second embodiment ...
FIG. 3 shows a cross section of the main part of the sealing device 1 according to the second embodiment of the present invention. The sealing device 1 is used, for example, as a seal for a hub bearing in a bearing portion in a vehicle wheel suspension device, and is configured as follows.

すなわち先ず、上記ベアリング部における密封装置取付部材であるベアリング外輪（図示せず）の内周側に嵌着される金属等剛材製の取付環２が設けられており、この取付環２にゴム状弾性材製の弾性体３が加硫接着されており、この弾性体３に複数のシールリップが一体成形されており、この複数のシールリップが、上記ベアリング部における相対回転部材でありかつ摺動の相手部材であるハブ９の軸方向端面部９ａに摺動自在に密接する外周側のサイドリップ６と、ハブ９の軸方向端面部９ａと周面部（外周面）９ｂとを連続させる断面円弧状の曲面部９ｃに摺動自在に密接する内周側のサイドリップ（中間リップとも称する）１０と、ハブ９の周面部９ｂに摺動自在に密接する内向きのグリースリップ１１とによって構成されている。   That is, first, a mounting ring 2 made of a rigid material such as a metal is provided on the inner peripheral side of a bearing outer ring (not shown) which is a sealing device mounting member in the bearing portion. An elastic body 3 made of a shaped elastic material is vulcanized and bonded, and a plurality of seal lips are integrally formed on the elastic body 3, and the plurality of seal lips are relative rotating members in the bearing portion and are slidable. A cross-section in which the outer side lip 6 slidably in close contact with the axial end surface portion 9a of the hub 9, which is a moving member, and the axial end surface portion 9a of the hub 9 and the peripheral surface portion (outer peripheral surface) 9b are continuous. An inner peripheral side lip (also referred to as an intermediate lip) 10 slidably in close contact with the arcuate curved surface portion 9c and an inward grease lip 11 slidably in close contact with the peripheral surface 9b of the hub 9 are configured. Has been.

上記３本のシールリップのうち、外周側および内周側のサイドリップ６，１０はそれぞれ、ベアリング外部の泥水やダスト等の異物がベアリング内部へ侵入しないようにこれをシールするものであって、その機能からして外向き構造とされ、その基端から先端へかけて径寸法が徐々に拡大するように形成されている。   Of the three seal lips, the outer lip and inner lip side lips 6 and 10 respectively seal the foreign matter such as muddy water and dust outside the bearing from entering the bearing, In view of its function, it has an outward structure and is formed so that its diameter gradually increases from its proximal end to its distal end.

また、このサイドリップ６，１０はそれぞれ、その先端面６ａ，１０ａが内周面６ｂ，１０ｂに対して斜め（鈍角）に交差する断面直線状に形成されており、これによりサイドリップ６，１０はそれぞれ、その摺動部先端頂角θ３，θ４の大きさが９０度よりも大きくかつ１１０度以下の角度（９０°＜θ３≦１１０°，９０°＜θ４≦１１０°、例えば約１００°）に形成されている。摺動部先端頂角θ３，θ４は、サイドリップ６，１０の断面形状において、サイドリップ６，１０の先端面６ａ，１０ａと内周面６ｂ，１０ｂとがなす角度である。 Further, the side lips 6 and 10 are formed in a straight cross-sectional shape in which the front end surfaces 6a and 10a intersect obliquely (obtuse angles) with respect to the inner peripheral surfaces 6b and 10b, respectively. Are respectively angles of the sliding portion tip apex angles θ 3 and θ 4 that are larger than 90 degrees and 110 degrees or less (90 ° <θ 3 ≦ 110 °, 90 ° <θ 4 ≦ 110 °, for example, About 100 °). The sliding portion tip apex angles θ 3 and θ 4 are angles formed by the tip surfaces 6 a and 10 a of the side lips 6 and 10 and the inner peripheral surfaces 6 b and 10 b in the cross-sectional shape of the side lips 6 and 10.

上記構成を備えた密封装置１を実機に装着すると、ハブ９がサイドリップ６，１０に対して相対に軸方向変位してハブ９に対するサイドリップ６，１０のしめしろの大きさが変化したり、ハブ９がサイドリップ６，１０に対して相対に径方向（軸直角方向）変位して軸偏心が発生したり、ハブ９がサイドリップ６，１０に対して相対に揺動変位していわゆる面振れが発生したり、あるいはこれらが複合して発生したりするが、上記密封装置１は上記構成により以下の作用効果を奏する点に特徴を有している。   When the sealing device 1 having the above configuration is mounted on an actual machine, the hub 9 is axially displaced relative to the side lips 6 and 10 to change the size of the interference between the side lips 6 and 10 with respect to the hub 9. The hub 9 is displaced in the radial direction (perpendicular to the axis) relative to the side lips 6 and 10 to generate shaft eccentricity, or the hub 9 is oscillated and displaced relative to the side lips 6 and 10. Although the surface runout or a combination thereof occurs, the sealing device 1 is characterized in that it has the following operational effects by the above configuration.

すなわち、上記構成の密封装置１においては、サイドリップ６，１０の摺動部先端頂角θ３，θ４がそれぞれ９０度よりも大きな角度に形成されているために、サイドリップ６，１０先端のボリュームが従来よりも実質的に増大せしめられている。これは、摺動部先端頂角が９０度以下の場合と比較して、サイドリップ６，１０の先端面６ａ，１０ａがサイドリップ６，１０の先端方向（長手方向）に突出した形状に形成されているからである。したがって、サイドリップ６，１０が変形しにくく、その接触状態が安定したものとされているために、しめしろの変化や面振れの発生等の悪条件下においてもサイドリップ６，１０の応力分布を適正に保つことができる。したがって、サイドリップ６，１０の接触面圧ピーク値が極端に小さくなって密封性能が極端に低下するのを防止することができ、これにより密封性能を安定化させることができる。また、サイドリップ６，１０先端の接触状態が安定すれば、サイドリップ６，１０先端の浮き上がりを防止することができるために、この点からも密封性能を安定化させることができる。 In other words, in the sealing device 1 having the above-described configuration, the tip end angles θ 3 and θ 4 of the sliding portions of the side lips 6 and 10 are formed at angles larger than 90 degrees, respectively. This volume has been substantially increased compared to the conventional volume. This is because the front end surfaces 6a and 10a of the side lips 6 and 10 protrude in the front end direction (longitudinal direction) of the side lips 6 and 10 as compared with the case where the sliding portion apex angle is 90 degrees or less. Because it is. Accordingly, since the side lips 6 and 10 are not easily deformed and the contact state thereof is stable, the stress distribution of the side lips 6 and 10 even under adverse conditions such as changes in interference and occurrence of surface runout. Can be kept appropriate. Therefore, the contact surface pressure peak value of the side lips 6 and 10 can be prevented from becoming extremely small and the sealing performance can be prevented from being extremely lowered, whereby the sealing performance can be stabilized. Further, if the contact state of the tips of the side lips 6 and 10 is stabilized, the tip of the side lips 6 and 10 can be prevented from being lifted, so that the sealing performance can be stabilized also in this respect.

また、上記密封装置１においては併せて、サイドリップ６，１０の摺動部先端頂角θ３，θ４が１１０度以下の角度に設定されているために、摺動部先端６ｃ、１０ｃに極端な応力集中が発生するのを防止することができ、よってサイドリップ６，１０の耐久性が低下するのを防止することができる。 In addition, in the sealing device 1, the sliding portion tip apex angles θ 3 and θ 4 of the side lips 6 and 10 are set to an angle of 110 degrees or less. It is possible to prevent the occurrence of extreme stress concentration, and thus it is possible to prevent the durability of the side lips 6 and 10 from being lowered.

本発明の密封装置は、上記したように自動車用車輪懸架装置におけるベアリング部にハブベアリング用シールとして用いられるが、そのほか汎用機械のシール部等に広く用いられる。   As described above, the sealing device of the present invention is used as a seal for a hub bearing in a bearing portion in an automobile wheel suspension, but is also widely used for a seal portion of a general-purpose machine.

本発明の第一実施例に係る密封装置の要部断面図Sectional drawing of the principal part of the sealing device which concerns on 1st Example of this invention. （Ａ）は同密封装置の軸方向変位前の状態を示す要部断面図、（Ｂ）は同密封装置の軸方向変位時の状態を示す要部断面図、（Ｃ）は比較例に係る密封装置の軸方向変位前の状態を示す要部断面図、（Ｄ）は同密封装置の軸方向変位時の状態を示す要部断面図(A) is principal part sectional drawing which shows the state before the axial direction displacement of the sealing device, (B) is principal part sectional drawing which shows the state at the time of the axial direction displacement of the sealing device, (C) concerns on a comparative example. Cross-sectional view of the main part showing the state before the axial displacement of the sealing device, (D) is a cross-sectional view of the main part showing the state of the sealing device during the axial displacement. 本発明の第二実施例に係る密封装置の要部断面図Sectional drawing of the principal part of the sealing device which concerns on 2nd Example of this invention. 従来例に係る密封装置の要部断面図Sectional drawing of the principal part of the sealing device which concerns on a prior art example （Ａ）（Ｂ）とも同密封装置におけるサイドリップ先端部の拡大断面図(A) Enlarged sectional view of the side lip tip in the same sealing device for both (A) and (B)

符号の説明Explanation of symbols

１ 密封装置
２ 取付環
３ 弾性体
４ スリンガー（相手部材）
５ フランジ部
５ａ，９ａ 軸方向端面部
６，１０ サイドリップ
６ａ，１０ａ 先端面
６ｂ，１０ｂ 内周面
６ｃ，１０ｃ 摺動部先端
７ 筒部
７ａ，９ｂ 周面部
８ ダストリップ
９ ハブ（相手部材）
９ｃ 曲面部
１１ グリースリップ DESCRIPTION OF SYMBOLS 1 Sealing device 2 Mounting ring 3 Elastic body 4 Slinger (mating member)
5 Flange portion 5a, 9a Axial end surface portion 6, 10 Side lip 6a, 10a End surface 6b, 10b Inner circumferential surface 6c, 10c Sliding portion distal end 7 Cylindrical portion 7a, 9b Peripheral surface portion 8 Dustrip 9 Hub (partner member)
9c Curved surface part 11 Grease lip

Claims (2)

相手部材（４）（９）の軸方向端面部（５ａ）（９ａ）または曲面部（９ｃ）に摺動自在に密接するサイドリップ（６）（１０）を有する密封装置（１）において、
前記サイドリップ（６）（１０）の摺動部先端頂角（θ３）（θ４）の大きさを９０度よりも大きな角度に設定したことを特徴とする密封装置。 In the sealing device (1) having side lips (6) and (10) slidably in close contact with the axial end surface portions (5a) (9a) or the curved surface portions (9c) of the mating members (4) and (9),
The sealing device characterized in that the size of the apex angle (θ 3 ) (θ 4 ) of the sliding portion of the side lip (6) (10) is set to an angle larger than 90 degrees. 相手部材（４）（９）の軸方向端面部（５ａ）（９ａ）または曲面部（９ｃ）に摺動自在に密接するサイドリップ（６）（１０）を有する密封装置（１）において、
前記サイドリップ（６）（１０）の摺動部先端頂角（θ３）（θ４）の大きさを９０度よりも大きくかつ１１０度以下の角度に設定したことを特徴とする密封装置。 In the sealing device (1) having side lips (6) and (10) slidably in close contact with the axial end surface portions (5a) (9a) or the curved surface portions (9c) of the mating members (4) and (9),
The sealing device characterized in that the sliding portion tip apex angle (θ 3 ) (θ 4 ) of the side lip (6) (10) is set to an angle greater than 90 degrees and 110 degrees or less.
JP2003320656A 2003-09-12 2003-09-12 Sealing device Expired - Lifetime JP4240217B2 (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009115110A (en) * 2007-11-01 2009-05-28 Nok Corp Sealing device
JP2009216138A (en) * 2008-03-07 2009-09-24 Jtekt Corp Sealing device for bearing
JP2009216139A (en) * 2008-03-07 2009-09-24 Jtekt Corp Sealing device for bearing
JP2014109354A (en) * 2012-12-04 2014-06-12 Nok Corp Seal device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009115110A (en) * 2007-11-01 2009-05-28 Nok Corp Sealing device
JP2009216138A (en) * 2008-03-07 2009-09-24 Jtekt Corp Sealing device for bearing
JP2009216139A (en) * 2008-03-07 2009-09-24 Jtekt Corp Sealing device for bearing
JP2014109354A (en) * 2012-12-04 2014-06-12 Nok Corp Seal device

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