JP2014005851A - Bearing sealing device - Google Patents

Bearing sealing device Download PDF

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Publication number
JP2014005851A
JP2014005851A JP2012140318A JP2012140318A JP2014005851A JP 2014005851 A JP2014005851 A JP 2014005851A JP 2012140318 A JP2012140318 A JP 2012140318A JP 2012140318 A JP2012140318 A JP 2012140318A JP 2014005851 A JP2014005851 A JP 2014005851A
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Prior art keywords
lip
sealing device
bearing
bearing sealing
seal
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JP2012140318A
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JP6074171B2 (en
Inventor
Kazuo Komori
和雄 小森
Takayuki Kawamura
隆之 川村
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring
    • F16C33/7883—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

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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)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a bearing sealing device in which torque can be reduced and a sealing performance can be improved compatibly.SOLUTION: The bearing sealing device is configured to seal an annular space between inner and outer rings 1 and 2 of a bearing and includes a seal body 3 provided in the outer ring 2, and lips 4, 5, and 6 extending from the seal body 3 in contact with a first seal plate 7 fitted to the inner ring 1. A chlorinated layer is formed on a top layer of the lips, and top layer hardness of the chlorinated layer is made higher than internal hardness of the lips. Thus, a friction coefficient of the lips is reduced rather than the lips to which chlorination processing is not applied, and torque is reduced rather than the prior arts. Since only a surface of the lips is modified, influences on lip followability or reactive forces are reduced and the sealing performance may also be ensured.

Description

この発明は、軸受密封装置に関し、低トルク化とシール性能向上の両立を図る技術に関する。   The present invention relates to a bearing sealing device, and relates to a technique for achieving both a reduction in torque and an improvement in sealing performance.

車輪用軸受において、転がり抵抗に占めるシールのリップ摺動抵抗の比率は高く、シールの低トルク化の要求が高まっている。
この背景の中、リップ反力の調整やグリースリップの非接触化などにより、低トルク化を図る技術を提案している（特許文献１）。 In wheel bearings, the ratio of the lip sliding resistance of the seal to the rolling resistance is high, and the demand for lower torque of the seal is increasing.
Against this background, a technique for reducing the torque by adjusting the lip reaction force or making the grease lip non-contact has been proposed (Patent Document 1).

特開２０１０−１９６９号公報JP 2010-1969

前記特許文献１では、リップ反力を下げることで低トルク化を図ることができるものの、トルクとシール性能は相反する関係にあるため、シール性が低下する可能性がある。したがって、シール性能が低下することにより、軸受内部に泥水が浸入し、軸受が短寿命になることが懸念される。   In Patent Document 1, although the torque can be reduced by lowering the lip reaction force, the torque and the sealing performance are in a contradictory relationship, so that the sealing performance may be reduced. Therefore, there is a concern that the sealing performance is deteriorated, so that muddy water enters the inside of the bearing and the bearing life is shortened.

この発明の目的は、低トルク化とシール性能向上の両立を図ることができる軸受密封装置を提供することである。   An object of the present invention is to provide a bearing sealing device capable of achieving both a reduction in torque and an improvement in sealing performance.

この発明の軸受密封装置は、軸受の内外輪間の環状空間を密封する軸受密封装置であって、前記内外輪のいずれか一方に設けられるシール本体と、このシール本体から延び前記内外輪のいずれか他方に接するリップとを有し、このリップの表層に、塩素化された層を有し、当該塩素化された層の表層硬さが同リップの内部硬さよりも高いことを特徴とする。ここで、塩素化処理とは、ゴムの成分、例えばジエン系ゴムの二重結合を切断して、塩素原子を導入するものであり、その結果、ゴムの表層に形成される層のことを「塩素化された層」と定義する。
従来における、一酸化二塩素を主成分とし、酢酸エチルを溶媒とした液による塩素化処理は、ゴムの硬化処理として公知であったが、それは例えばワイパーなどに用いられるゴムであり、本発明のような密封部材における弾性部材に適用させるものではなかった。それは一般的に密封部材における弾性部材は、密封装置という機能上、弾性部材を硬化させることはシール性を損なう恐れがあるため不向きだと考えられていたためである。 A bearing sealing device according to the present invention is a bearing sealing device that seals an annular space between inner and outer rings of a bearing, and includes a seal main body provided in one of the inner and outer rings, and any of the inner and outer rings extending from the seal main body. The lip is in contact with the other lip, and the surface layer of the lip has a chlorinated layer, and the surface hardness of the chlorinated layer is higher than the internal hardness of the lip. Here, the chlorination treatment is to introduce a chlorine atom by cutting a double component of a rubber component, for example, a diene rubber, and as a result, a layer formed on the surface layer of the rubber is referred to as “ It is defined as “chlorinated layer”.
The conventional chlorination treatment with a liquid mainly composed of dichlorine monoxide and ethyl acetate as a solvent has been known as a rubber curing treatment, but it is a rubber used for, for example, a wiper. It was not applied to the elastic member in such a sealing member. This is because it is generally considered that the elastic member in the sealing member is unsuitable for curing the elastic member because of the function of the sealing device, since the sealing performance may be impaired.

この構成によると、一酸化二塩素を主成分とし酢酸エチルを溶媒とした液に、リップを浸漬する塩素化処理を施すことで、リップ表面を改質して、リップの内部硬さよりもこのリップの表層硬さを高くし得る。リップの表層硬さを高くすることで、リップ摺動面の微小凸部への接触面積（真実接触面積）が減る。その結果、摩擦係数が低下すると共に、いわゆる凸へのゴム食い込みによる引っ掛り（粘着）が減り、従来技術よりも低トルク化を図れる。またリップ表面のみの改質であるため、リップ追従性や反力への影響が小さく、シール性をも確保することができる。つまりリップ表面は、化学処理により硬化されるが、内部はゴム本来の特性を有したままにでき、したがってシールとしての弾性も有することで、シール性を確保できる。リップに例えばフッ素系処理剤等の低摩擦コーティングを施したり、ダイヤモンドライクカーボン膜（略称；ＤＬＣ膜）を施すものよりも、前記塩素化処理は処理自体が簡単で短時間で行うことができる。よって低摩擦コーティング等をリップに施すよりも製造コストの低減を図れる。   According to this configuration, the lip surface is modified by immersing the lip in a solution containing dichlorine monoxide as the main component and ethyl acetate as the solvent, thereby improving the lip surface rather than the internal hardness of the lip. The surface layer hardness can be increased. By increasing the surface hardness of the lip, the contact area (true contact area) to the minute convex portion of the lip sliding surface is reduced. As a result, the friction coefficient is lowered, and the so-called protrusion (adhesion) due to the biting of the rubber is reduced, so that the torque can be reduced as compared with the prior art. Further, since only the lip surface is modified, the influence on the lip following property and reaction force is small, and the sealing property can be secured. In other words, the lip surface is hardened by chemical treatment, but the inside can be kept with the original characteristics of rubber, and therefore, the sealing property can be ensured by having elasticity as a seal. The chlorination treatment is simpler and can be performed in a shorter time than when the lip is provided with a low friction coating such as a fluorine treatment agent or a diamond-like carbon film (abbreviation: DLC film). Therefore, the manufacturing cost can be reduced as compared with the case where a low friction coating or the like is applied to the lip.

前記塩素化された層が、一酸化二塩素を主成分とし、酢酸エチルを溶媒とした液に非極性溶媒を加えた液に浸漬して成るものであっても良い。一酸化二塩素を主成分とし酢酸エチルを溶媒とした液に、ある弾性材料から成る試験片を長時間浸漬させると、この試験片が不所望に膨張した。膨張したリップ等を用いると、シールの緊迫力が増加しトルクが増加する。前記のように一酸化二塩素を酢酸エチルで溶媒させた液を、非極性溶媒で希釈した液に、リップを浸漬する塩素化処理を施すことにより、リップ等が膨張し難くシールの緊迫力の増加を緩和できる。したがって、非極性溶媒で希釈した塩素化処理を施す場合、塩素化処理を施さないものや、非極性溶媒で希釈しない通常の塩素化処理を施したものより、低トルク化を図ることができる。
前記非極性溶媒として石油ベンジンを適用しても良い。前記非極性溶媒の例として、ヘキサン、ベンジン、トルエン、ジエチルエーテル、石油ベンジンなどが挙げられ、その中で、コストと性能のバランスで石油ベンジンが望ましい。
前記リップの表層硬さを同リップの内部硬さよりも、国際ゴム硬さ（ＩＲＨＤ）の単位で２〜５ポイント高くしたものであっても良い。
前記液による浸漬で、リップ部に使用するゴム材料（ジエン系）を国際ゴム硬さの単位で２〜５ポイント高くしたものであっても良い。
前記シール本体およびリップがニトリルゴムから成るものとしても良い。
前記軸受として、車輪用軸受が適用されても良い。この場合、低トルク化を図れると共に、車輪用軸受内部に泥水等が不所望に浸入することを防止しもって軸受寿命を延ばすことができる。 The chlorinated layer may be formed by immersing in a liquid obtained by adding a nonpolar solvent to a liquid containing dichlorine monoxide as a main component and ethyl acetate as a solvent. When a test piece made of an elastic material was immersed in a solution containing dichlorine monoxide as a main component and ethyl acetate as a solvent for a long time, the test piece expanded undesirably. When an expanded lip or the like is used, the tightening force of the seal increases and the torque increases. By applying a chlorination treatment that immerses the lip in a solution obtained by diluting dichlorine monoxide with ethyl acetate as described above and immersing the lip in a solution obtained by diluting with a nonpolar solvent, the lip or the like is less likely to expand, and the sealing force The increase can be mitigated. Therefore, when the chlorination treatment diluted with the nonpolar solvent is performed, the torque can be reduced as compared with those not subjected to the chlorination treatment and those subjected to the normal chlorination treatment not diluted with the nonpolar solvent.
Petroleum benzine may be applied as the nonpolar solvent. Examples of the nonpolar solvent include hexane, benzine, toluene, diethyl ether, petroleum benzine, etc. Among them, petroleum benzine is desirable in terms of a balance between cost and performance.
The surface hardness of the lip may be 2 to 5 points higher in terms of international rubber hardness (IRHD) than the internal hardness of the lip.
The rubber material (diene type) used for the lip portion may be increased by 2 to 5 points in units of international rubber hardness by immersion with the liquid.
The seal body and the lip may be made of nitrile rubber.
A wheel bearing may be applied as the bearing. In this case, torque can be reduced, and muddy water or the like can be prevented from entering undesirably inside the wheel bearing, thereby extending the bearing life.

前記軸受密封装置は、前記内外輪のおける回転側部材の周面に嵌合する円筒部およびこの円筒部の端部から立ち上がる立板部を含む断面Ｌ字状の第１のシール板と、この第１のシール板に対向し、前記内外輪における固定側部材に嵌合される断面Ｌ字状の第２のシール板とを有し、前記リップは、前記第２のシール板に固着される前記シール本体から延び、且つ、前記第１のシール板の立板部に摺接するサイドリップと、前記第１のシール板の円筒部に摺接するラジアルリップとを有するものとしても良い。
この構成によると、第１，第２のシール板が対向し、サイドリップおよびラジアルリップが摺接するため、密封性能が優れたものになる。 The bearing sealing device includes a first seal plate having an L-shaped cross section including a cylindrical portion that fits on a circumferential surface of a rotation-side member of the inner and outer rings, and a standing plate portion that rises from an end portion of the cylindrical portion, A second seal plate facing the first seal plate and fitted to a stationary member in the inner and outer rings and having an L-shaped cross section, and the lip is fixed to the second seal plate A side lip extending from the seal main body and slidably contacting the upright plate portion of the first seal plate, and a radial lip slidably contacting the cylindrical portion of the first seal plate may be provided.
According to this configuration, the first and second sealing plates face each other, and the side lip and the radial lip are in sliding contact with each other, so that the sealing performance is excellent.

前記サイドリップは、第２のシール板における径方向の内外に２枚並ぶ構造としても良い。この場合、２枚のサイドリップにより耐泥水性の向上を図ることができる。
前記リップを３枚のリップから成る３リップ構造としても良い。
前記リップを２枚のリップから成る２リップ構造としても良い。 Two side lips may be arranged side by side in the radial direction of the second seal plate. In this case, muddy water resistance can be improved by two side lips.
The lip may have a three-lip structure including three lips.
The lip may have a two-lip structure composed of two lips.

前記第１のシール板におけるリップの摺動面に、微小な凹部を設けても良い。これら凹部に、例えばリップに塗布されたグリースが保持される結果、リップの摺動抵抗の低減を図ることができる。これにより低トルク化をより図れる。
前記凹部の粗さをＲｚ＝１〜８μｍとしても良い。 A minute recess may be provided on the sliding surface of the lip in the first seal plate. For example, grease applied to the lip is held in these recesses, so that the sliding resistance of the lip can be reduced. Thereby, the torque can be further reduced.
The roughness of the recess may be Rz = 1 to 8 μm.

前記リップにグリースが塗布され、このリップに塗布するグリースの基油動粘度を、軸受内部に封入するグリースの基油動粘度よりも小さくしても良い。この場合、リップの摺動抵抗の低減を図れ、低トルク化をより図れる。
前記リップに塗布するグリースの基油動粘度を５ｍｍ２／Ｓ（１００℃）以下としてもよい。 Grease is applied to the lip, and the base oil dynamic viscosity of the grease applied to the lip may be smaller than the base oil dynamic viscosity of the grease sealed in the bearing. In this case, the sliding resistance of the lip can be reduced and the torque can be further reduced.
The base oil kinematic viscosity of the grease applied to the lip may be 5 mm 2 / S (100 ° C.) or less.

この発明の軸受密封装置は、軸受の内外輪間の環状空間を密封する軸受密封装置であって、前記内外輪のいずれか一方に設けられるシール本体と、このシール本体から延び前記内外輪のいずれか他方に接するリップとを有し、このリップの表層に、塩素化された層を有し、当該塩素化された層の表層硬さが同リップの内部硬さよりも高いため、低トルク化とシール性能向上の両立を図ることができる。   A bearing sealing device according to the present invention is a bearing sealing device that seals an annular space between inner and outer rings of a bearing, and includes a seal main body provided in one of the inner and outer rings, and any of the inner and outer rings extending from the seal main body. The lip is in contact with the other lip, and the surface layer of the lip has a chlorinated layer, and the surface hardness of the chlorinated layer is higher than the internal hardness of the lip. It is possible to improve the sealing performance.

この発明の第１の実施形態に係る軸受密封装置の断面図である。1 is a cross-sectional view of a bearing sealing device according to a first embodiment of the present invention. この発明の他の実施形態に係る軸受密封装置の要部の断面図である。It is sectional drawing of the principal part of the bearing sealing device which concerns on other embodiment of this invention. この発明のさらに他の実施形態に係る軸受密封装置の断面図である。It is sectional drawing of the bearing sealing device which concerns on other embodiment of this invention. この発明のさらに他の実施形態に係る軸受密封装置の断面図である。It is sectional drawing of the bearing sealing device which concerns on other embodiment of this invention. この発明のさらに他の実施形態に係る軸受密封装置の断面図である。It is sectional drawing of the bearing sealing device which concerns on other embodiment of this invention. この発明のさらに他の実施形態に係る軸受密封装置の断面図である。It is sectional drawing of the bearing sealing device which concerns on other embodiment of this invention. この発明のいずれかの軸受密封装置を用いた車輪用軸受の断面図である。It is sectional drawing of the bearing for wheels using the bearing sealing device in any one of this invention. 試験片に対する回転速度と摩擦係数との関係を、塩素化処理の有無で比較して示す図である。It is a figure which compares and shows the relationship between the rotational speed with respect to a test piece, and a friction coefficient by the presence or absence of a chlorination process. ゴムの物性変化を測定する測定装置を概略示す図である。It is a figure which shows roughly the measuring apparatus which measures the physical property change of rubber | gum. ゴムの物性変化を、塩素化処理の有無で比較して示す図である。It is a figure which compares and shows the physical-property change of rubber | gum by the presence or absence of chlorination treatment. 各種の軸受密封装置の回転速度と回転トルクとの関係を示す図である。It is a figure which shows the relationship between the rotational speed of various bearing sealing apparatuses, and rotational torque.

この発明の第１の実施形態に係る軸受密封装置を図１と共に説明する。以下の説明は、軸受密封装置の製造方法についての説明をも含む。
図１に示すように、この実施形態に係る軸受密封装置は、軸受の内外輪１，２間における端部の環状空間を密封する。この軸受密封装置のシール本体３およびリップ４，５，６に、後述の塩素化処理が施されている。
第１，第２のシール板７，８について説明する。
軸受密封装置は、内輪１と外輪２に各々取付けられた第１および第２の環状のシール板７，８を有する。これら第１，第２のシール板７，８は、それぞれ鋼板製で、各々内輪１および外輪２に圧入状態に嵌合させることで取付けられている。第１，第２のシール板７，８は、各々円筒部９，１０と立板部１１，１２とで断面Ｌ字状に形成されて互いに対向する。第１のシール板７の立板部１２は、第２のシール板８の立板部１２よりも軸受外方側に配設される。 A bearing sealing device according to a first embodiment of the present invention will be described with reference to FIG. The following description also includes a description of a method for manufacturing the bearing sealing device.
As shown in FIG. 1, the bearing sealing device according to this embodiment seals the annular space at the end between the inner and outer rings 1 and 2 of the bearing. The seal body 3 and the lips 4, 5 and 6 of this bearing sealing device are subjected to a chlorination treatment which will be described later.
The first and second seal plates 7 and 8 will be described.
The bearing sealing device has first and second annular seal plates 7 and 8 attached to the inner ring 1 and the outer ring 2, respectively. These first and second seal plates 7 and 8 are each made of a steel plate and attached by being fitted into the inner ring 1 and the outer ring 2 in a press-fitted state. The first and second seal plates 7 and 8 are formed in a L-shaped cross section by the cylindrical portions 9 and 10 and the standing plate portions 11 and 12, respectively, and face each other. The standing plate portion 12 of the first seal plate 7 is disposed on the bearing outer side with respect to the standing plate portion 12 of the second seal plate 8.

第２のシール板８の立板部１２は、外径側板部１２ａと、傾斜部１２ｂと、内径側板部１２ｃとを有する。すなわち外径側板部１２ａは、第２のシール板８における円筒部１０の基端から、径方向内方に延びる環状板である。傾斜部１２ｂは、外径側板部１２ａの内径側端から径方向内方に向かうに従って軸受外方側に至るように傾斜する断面形状に形成される。内径側板部１２ｃは、傾斜部１２ｂの内径側端から径方向内方に延びる環状板である。   The standing plate portion 12 of the second seal plate 8 has an outer diameter side plate portion 12a, an inclined portion 12b, and an inner diameter side plate portion 12c. That is, the outer diameter side plate portion 12 a is an annular plate that extends radially inward from the base end of the cylindrical portion 10 in the second seal plate 8. The inclined portion 12b is formed in a cross-sectional shape that is inclined so as to reach the outer side of the bearing as it goes radially inward from the inner diameter side end of the outer diameter side plate portion 12a. The inner diameter side plate portion 12c is an annular plate extending radially inward from the inner diameter side end of the inclined portion 12b.

第２のシール板８の円筒部１０は、軸受内方側から外方側に沿って順次、基端部１０ａと、傾斜部１０ｂと、先端部１０ｃとを有する。基端部１０ａは、前記外径側板部１２ａの基端から、軸受外方側に延びるリング状部材から成る。傾斜部１０ｂは、基端部１０ａの軸方向先端から径方向内方に向かうに従って軸受外方側に至るように傾斜する断面形状に形成される。先端部１０ｃは、傾斜部１０ｂの先端から軸方向に延びる。基端部１０ａの軸方向先端と傾斜部１０ｂの基端との内径側境界部に、環状凹部が形成されると共に、傾斜部１０ｂおよび先端部１０ｃが、基端部１０ａよりも薄肉に形成される。   The cylindrical portion 10 of the second seal plate 8 has a proximal end portion 10a, an inclined portion 10b, and a distal end portion 10c sequentially from the bearing inner side to the outer side. The base end portion 10a is formed of a ring-shaped member that extends outward from the base end of the outer diameter side plate portion 12a. The inclined portion 10b is formed in a cross-sectional shape that is inclined so as to reach the outer side of the bearing as it goes radially inward from the axial tip of the base end portion 10a. The tip portion 10c extends in the axial direction from the tip of the inclined portion 10b. An annular recess is formed at the inner diameter side boundary between the axial tip of the base end portion 10a and the base end of the inclined portion 10b, and the inclined portion 10b and the tip end portion 10c are formed thinner than the base end portion 10a. The

傾斜部１０ｂの外周面および先端部１０ｃの外周面に、円筒部１０の外周面よりも半径方向外方に突出するシール本体３（後述する）の一部である突起部１３を設けている。円筒部１０の外周面が外輪内周面に嵌合している状態で、前記シール本体３のうち半径方向外方に突出する突起部１３が、外輪内周面に強固に密着されるようになっている。   On the outer peripheral surface of the inclined portion 10b and the outer peripheral surface of the distal end portion 10c, a protruding portion 13 that is a part of a seal body 3 (described later) that protrudes radially outward from the outer peripheral surface of the cylindrical portion 10 is provided. In a state where the outer peripheral surface of the cylindrical portion 10 is fitted to the inner peripheral surface of the outer ring, the protruding portion 13 protruding outward in the radial direction in the seal body 3 is firmly attached to the inner peripheral surface of the outer ring. It has become.

シール本体３、リップ４，５，６について説明する。
第２のシール板８は、シール本体３と、サイドリップ４と、ダストリップ５と、グリースリップ６とを有する。サイドリップ４、ダストリップ５、およびグリースリップ６を、総称してリップ等またはリップと称す。これらシール本体３およびリップ等は、例えば、天然ゴム、ブタジエンゴム、ニトリルゴム等の弾性材料から成り、第２のシール板８に加硫接着されて一体に設けられる。但し、これらの弾性材料に必ずしも限定されるものではない。 The seal body 3 and the lips 4, 5, 6 will be described.
The second seal plate 8 has a seal body 3, a side lip 4, a dust lip 5, and a grease lip 6. The side lip 4, dust lip 5 and grease lip 6 are collectively referred to as a lip or the like or a lip. The seal body 3 and the lip are made of an elastic material such as natural rubber, butadiene rubber, nitrile rubber, and the like, and are vulcanized and bonded to the second seal plate 8 so as to be integrally provided. However, it is not necessarily limited to these elastic materials.

シール本体３は、第２のシール板８における、立板部１２の外側面、円筒部１０の内周面，先端面，および外周面にわたって連続して設けられる。なお図１では、シール本体３のうち、傾斜部１０ｂおよび先端部１０ｃの外周面に設けられる突起部１３が、外輪内周面内に入り込んでいるように表示されているが、この突起部１３は、外輪２への組込前の自然状態を示している。第２のシール板８を外輪２に組込後、前記突起部１３は、弾性変形された状態で基端部１０ａの外周面と略同一面で外輪内周面に圧入されている。これにより、異物等が、外輪内周面と第２のシール板８との間を介して侵入することを防止し得る。シール本体３は、先端部１０ｃの内周面，先端面，外周面、および傾斜部１０ｂの外周面を囲むように連続して設けられる。また前記先端面に設けられるシール本体３の一部は、第１のシール板７における立板部１２の外径側端に対し僅かな径方向すきまδ１をもって対峙させている。この径方向すきまδ１により、異物等が第１のシール板７とリップとの間を介して侵入することを効果的に阻止し得る。   The seal body 3 is provided continuously over the outer surface of the upright plate portion 12, the inner peripheral surface, the distal end surface, and the outer peripheral surface of the cylindrical portion 10 in the second seal plate 8. In FIG. 1, in the seal body 3, the protrusions 13 provided on the outer peripheral surfaces of the inclined portion 10 b and the tip portion 10 c are displayed so as to enter the inner peripheral surface of the outer ring. Indicates a natural state before incorporation into the outer ring 2. After the second seal plate 8 is assembled into the outer ring 2, the protruding portion 13 is press-fitted into the inner peripheral surface of the outer ring on the substantially same surface as the outer peripheral surface of the base end portion 10 a while being elastically deformed. As a result, foreign matter or the like can be prevented from entering between the inner peripheral surface of the outer ring and the second seal plate 8. The seal body 3 is continuously provided so as to surround the inner peripheral surface, the front end surface, the outer peripheral surface of the front end portion 10c, and the outer peripheral surface of the inclined portion 10b. Further, a part of the seal body 3 provided on the front end face is opposed to the outer diameter side end of the standing plate portion 12 in the first seal plate 7 with a slight radial clearance δ1. This radial clearance δ1 can effectively prevent foreign matter and the like from entering through between the first seal plate 7 and the lip.

サイドリップ４は、第１のシール板７の立板部１２に摺接する。このサイドリップ４は、シール本体３から軸方向外側に突出する基端側リップ部４ａと、この基端側リップ部４ａに繋がる先端側リップ部４ｂとを有する。基端側リップ部４ａ、先端側リップ部４ｂは、それぞれ径方向外方に向かうに従って軸受外方側に至るように傾斜する断面形状に形成される。但し、軸受軸心に対する先端側リップ部４ｂの傾斜角度は、基端側リップ部４ａの傾斜角度よりも大となるように規定され、両リップ部の繋ぎ部４ｃが屈曲するように形成されている。このようにサイドリップ４を傾斜状に形成すると共に、両リップ部４ａ，４ｂの繋ぎ部４ｃを屈曲させたことで、サイドリップ４は立板部１２に対し一定の押圧力で常に摺接する。また先端側リップ部４ｂは、断面長方形状に形成され、長方形状の角部４ｂａが立板部１２に摺接する。先端側リップ部４ｂの側面や先端面ではなく、角部４ｂａを摺接させることで、リップ部側面等を摺接させる場合よりも、摩擦係数を低減できて低トルク化を図れる。   The side lip 4 is in sliding contact with the upright plate portion 12 of the first seal plate 7. The side lip 4 has a base end side lip portion 4a protruding outward in the axial direction from the seal body 3, and a front end side lip portion 4b connected to the base end side lip portion 4a. The proximal end lip portion 4a and the distal end lip portion 4b are each formed in a cross-sectional shape that is inclined so as to reach the outer side of the bearing as it goes outward in the radial direction. However, the inclination angle of the distal end side lip portion 4b with respect to the bearing axis is defined to be larger than the inclination angle of the proximal end side lip portion 4a, and the connecting portion 4c of both lip portions is formed to be bent. Yes. In this way, the side lip 4 is formed in an inclined shape, and the connecting portion 4c between the lip portions 4a and 4b is bent, so that the side lip 4 is always in sliding contact with the standing plate portion 12 with a constant pressing force. The tip side lip portion 4b is formed in a rectangular cross section, and the rectangular corner portion 4ba is in sliding contact with the standing plate portion 12. By bringing the corner portion 4ba into sliding contact instead of the side surface or the leading end surface of the tip side lip portion 4b, the friction coefficient can be reduced and the torque can be reduced as compared with the case where the side surface of the lip portion is slid.

グリースリップ６とダストリップ５とは、シール本体３の内周側端から軸方向内外に二股に分岐して突出する。これらグリースリップ６およびダストリップ５は、それぞれ第１のシール板７の円筒部９に対し、ラジアル方向に摺接するいわゆるラジアルリップである。ダストリップ５は、先端側に向かうに従って肉厚が厚くなる断面形状で、且つ、径方向内方に向かうに従って軸受外方側に至るように傾斜する断面形状に形成される。グリースリップ６は、先端側に向かうに従って肉厚が薄くなる断面形状で、且つ、径方向内方に向かうに従って軸受内方側に至るように傾斜する断面形状に形成される。ダストリップ５，グリースリップ６は、それぞれ略長方形状の角部５ａ，６ａが円筒部９に摺接するようになっている。これらダストリップ５，グリースリップ６と円筒部９とで囲まれた環状空間にグリースが保持され、このグリースにより、リップ５，６の摩耗防止を図ると共に、異物等が軸受内部に侵入することを防止する。リップ５，６の各角部５ａ，６ａを摺接させることで、リップ先端面全体を摺接させる場合よりも、低トルク化を図れる。   The grease lip 6 and the dust lip 5 project from the inner peripheral side end of the seal body 3 by bifurcating inward and outward in the axial direction. The grease lip 6 and the dust lip 5 are so-called radial lips that are in sliding contact with the cylindrical portion 9 of the first seal plate 7 in the radial direction. The dust lip 5 is formed in a cross-sectional shape that increases in thickness toward the tip end side, and in a cross-sectional shape that inclines so as to reach the outer side of the bearing toward the inner side in the radial direction. The grease lip 6 is formed in a cross-sectional shape in which the thickness is reduced toward the distal end side, and in a cross-sectional shape that is inclined so as to reach the inner side of the bearing toward the inner side in the radial direction. The dust lip 5 and the grease lip 6 are configured such that the substantially rectangular corner portions 5 a and 6 a are in sliding contact with the cylindrical portion 9. Grease is held in an annular space surrounded by the dust lip 5 and the grease lip 6 and the cylindrical portion 9, and this grease prevents wear of the lips 5 and 6, and prevents foreign matter and the like from entering the bearing. To prevent. By bringing the corners 5a and 6a of the lips 5 and 6 into sliding contact with each other, torque can be reduced as compared with the case where the entire lip tip surface is brought into sliding contact.

塩素化処理について説明する。
シール本体３およびリップ４，５，６は、「Ｃｌ２Ｏ＋酢酸エチル」つまり一酸化二塩素を主成分とし酢酸エチルを溶媒とした液に浸漬する塩素化処理が施されている。ここで、塩素化処理とは、ゴムの成分、例えばジエン系ゴムの二重結合を切断して、塩素原子を導入するものであり、その結果、リップのゴムの表層に「塩素化された層」が形成される。この層は同リップの内部よりも塩素含有量が多く、また、内部硬さよりも硬いことを特徴とする。当該「塩素化された層」は、数μm〜数百μmの層を有していれば良い。なお、ゴムの表層を分析すれば、二重結合が消滅し、塩素原子が導入されていることを確かめることで、塩素化処理されているか否かを確かめることができる。この処理時間は、例えば、数秒〜数十秒である。混合比率は、酢酸エチル：９０〜９９．９ｗｔ％＋Ｃｌ２Ｏ：０．１〜１０ｗｔ％である。なお、この例では、第２のシール板８、シール本体３、およびリップの全体を「Ｃｌ２Ｏ＋酢酸エチル」に浸漬しているが、シール本体３およびリップを浸漬しても良いし、リップだけを浸漬しても良い。いずれにしてもリップは、前記塩素化処理が施されて、リップの表層硬さを同リップの内部硬さよりも高くしている。 The chlorination treatment will be described.
The seal body 3 and the lips 4, 5 and 6 are subjected to a chlorination treatment of “Cl 2 O + ethyl acetate”, that is, immersed in a solution containing dichlorine monoxide as a main component and ethyl acetate as a solvent. Here, the chlorination treatment is to introduce a chlorine atom by cutting a double component of a rubber component, for example, a diene rubber, and as a result, a chlorinated layer is formed on the surface layer of the lip rubber. Is formed. This layer has a higher chlorine content than the inside of the lip and is characterized by being harder than the internal hardness. The “chlorinated layer” only needs to have a layer of several μm to several hundred μm. If the surface layer of the rubber is analyzed, it can be confirmed whether the chlorination treatment has been performed by confirming that the double bond has disappeared and chlorine atoms have been introduced. This processing time is, for example, several seconds to several tens of seconds. Mixing ratio, ethyl acetate: 90~99.9wt% + Cl 2 O: is 0.1-10%. In this example, the second seal plate 8, the seal body 3, and the entire lip are immersed in “Cl 2 O + ethyl acetate”. However, the seal body 3 and the lip may be immersed, or the lip Only soaking may be used. In any case, the lip is subjected to the chlorination treatment so that the surface hardness of the lip is higher than the internal hardness of the lip.

具体的に、リップの表層硬さを同リップの内部硬さよりも、国際ゴム硬さで２ポイント以上５ポイント以下高くしている。前記「国際ゴム硬さ」（略称ＩＲＨＤ；International Rubber Hardness Degree）は、測定対象面に対し、圧子を一定の静荷重で一定時間押込み、変形量つまり基準面からの押込み深さを測定して数値化した値である。なおリップの表層硬さは、試験片表面に圧子を押込むことで測定し得る。   Specifically, the surface hardness of the lip is higher than the internal hardness of the lip by 2 to 5 points in terms of international rubber hardness. The “International Rubber Hardness Degree” (abbreviated as IRHD) is a numerical value obtained by indenting an indenter into a surface to be measured with a constant static load for a certain period of time and measuring a deformation amount, that is, an indentation depth from a reference surface. It is a converted value. The surface hardness of the lip can be measured by pressing an indenter into the surface of the test piece.

作用効果について説明する。
この構成によると、一酸化二塩素を主成分とし酢酸エチルを溶媒とした液に、少なくともリップを浸漬する塩素化処理を施す、換言すれば、ジエン系ゴムの分子中の二重結合を塩素化する処理を施すことで、リップ表面を改質して、リップの内部硬さよりもこのリップの表層硬さを高くし得る。リップの表層硬さを高くすることで、リップ摺動面の微小凸部への接触面積（真実接触面積）が減る。その結果、摩擦係数が低下すると共に、いわゆる凸へのゴム食い込みによる引っ掛り（粘着）が減り、従来技術よりも低トルク化を図れる。 The effect will be described.
According to this configuration, a chlorination treatment in which at least a lip is immersed in a liquid containing dichlorine monoxide as a main component and ethyl acetate as a solvent, in other words, chlorinating a double bond in a diene rubber molecule. By carrying out the treatment, the surface of the lip can be made higher than the internal hardness of the lip by modifying the lip surface. By increasing the surface hardness of the lip, the contact area (true contact area) to the minute convex portion of the lip sliding surface is reduced. As a result, the friction coefficient is lowered, and the so-called protrusion (adhesion) due to the biting of the rubber is reduced, so that the torque can be reduced as compared with the prior art.

またリップ表面のみの改質であるため、リップ追従性や反力への影響が小さく、シール性をも確保することができる。つまりリップ表面Ｓａは、化学処理により硬化されるが、内部Ｓｂはゴム本来の特性を有したままにでき、したがってシールとしての弾性も有することで、シール性を確保できる。リップに例えばフッ素系処理剤等の低摩擦コーティングを施したり、ＤＬＣ膜を施すものよりも、前記塩素化処理は処理自体が簡単で短時間で行うことができる。よって低摩擦コーティング等をリップに施すものよりも製造コストの低減を図れる。   Further, since only the lip surface is modified, the influence on the lip following property and reaction force is small, and the sealing property can be secured. That is, the lip surface Sa is hardened by chemical treatment, but the internal Sb can be kept with the original characteristics of rubber, and therefore has sealing elasticity, thereby ensuring sealing performance. The chlorination treatment is simpler and can be carried out in a shorter time than a lip having a low friction coating such as a fluorine treatment agent or a DLC film. Therefore, the manufacturing cost can be reduced as compared with the case where a low friction coating or the like is applied to the lip.

第１，第２のシール板７，８が対向し、サイドリップ４、ダストリップ５、およびグリースリップ６が摺接するため、密封性能が優れたものになる。また、第２のシール板８の円筒部１０が外輪内周面に圧入状態に嵌合している状態で、シール本体３のうち半径方向外方に突出する突起部１３が、外輪内周面に強固に密着される。これにより、異物等が、外輪内周面と第２のシール板８との間を介して侵入することを防止し得る。   Since the first and second seal plates 7 and 8 face each other and the side lip 4, the dust lip 5 and the grease lip 6 are in sliding contact with each other, the sealing performance is excellent. Further, in the state where the cylindrical portion 10 of the second seal plate 8 is press-fitted to the inner peripheral surface of the outer ring, the protruding portion 13 protruding outward in the radial direction of the seal body 3 is the inner peripheral surface of the outer ring. Firmly attached to the surface. As a result, foreign matter or the like can be prevented from entering between the inner peripheral surface of the outer ring and the second seal plate 8.

他の実施形態について説明する。
以下の説明においては、各形態で先行する形態で説明している事項に対応している部分には同一の参照符を付し、重複する説明を略する。構成の一部のみを説明している場合、構成の他の部分は、特に記載のない限り先行して説明している形態と同様とする。同一の構成から同一の作用効果を奏する。実施の各形態で具体的に説明している部分の組合せばかりではなく、特に組合せに支障が生じなければ、実施の形態同士を部分的に組合せることも可能である。 Another embodiment will be described.
In the following description, the same reference numerals are given to the portions corresponding to the matters described in the preceding forms in each embodiment, and the overlapping description is omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in advance unless otherwise specified. The same effect is obtained from the same configuration. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

リップは、「Ｃｌ２Ｏ＋酢酸エチル」に非極性溶媒を加えた液に浸漬して成るものであっても良い。前記非極性溶媒の例として、ヘキサン、ベンジン、トルエン、ジエチルエーテル、石油ベンジンなどが挙げられ、その中で、コストと性能のバランスで石油ベンジンが望ましい。この例では、Ｃｌ２Ｏ＋酢酸エチルに対して、例えば、石油ベンジンを２〜４倍で希釈する。ところで一酸化二塩素を主成分とし酢酸エチルを溶媒とした液に、ある弾性材料から成る試験片を長時間（例えば６０秒）浸漬させると、この試験片が不所望に膨張した。膨張したリップ等を用いると、シールの緊迫力が増加しトルクが増加する。
前記のように一酸化二塩素を酢酸エチルで溶媒させた液を、石油ベンジンで希釈した液に、リップを浸漬する塩素化処理を施すことにより、リップ等が膨張し難くシールの緊迫力の増加を緩和できる。したがって、石油ベンジンで希釈した塩素化処理を施す場合、塩素化処理を施さないものや、石油ベンジンで希釈しない通常の塩素化処理を施したものより、低トルク化を図ることができる。 The lip may be formed by immersing in a solution obtained by adding a nonpolar solvent to “Cl 2 O + ethyl acetate”. Examples of the nonpolar solvent include hexane, benzine, toluene, diethyl ether, petroleum benzine, etc. Among them, petroleum benzine is desirable in terms of a balance between cost and performance. In this example, for example, petroleum benzine is diluted 2 to 4 times with respect to Cl 2 O + ethyl acetate. By the way, when a test piece made of an elastic material was immersed in a solution containing dichlorine monoxide as a main component and ethyl acetate as a solvent for a long time (for example, 60 seconds), the test piece expanded undesirably. When an expanded lip or the like is used, the tightening force of the seal increases and the torque increases.
By applying a chlorination treatment that immerses the lip in a solution obtained by diluting dichlorine monoxide with ethyl acetate as described above and immersing the lip in a solution diluted with petroleum benzine, the lip or the like hardly expands, and the seal tension increases. Can be relaxed. Therefore, when the chlorination treatment diluted with petroleum benzine is performed, the torque can be reduced as compared with those not subjected to chlorination treatment or those subjected to normal chlorination treatment not diluted with petroleum benzine.

図２に示すように、第１のシール板７における、グリースリップ６，ダストリップ５，サイドリップ（図示せず）の摺動面に、複数の微小な凹部１４を設けても良い。その他第１の実施形態と同様に、リップ等に塩素化処理が施されている。前記凹部１４の粗さを、例えば、Ｒｚ＝１〜８μｍとしている。これら凹部１４に、例えばリップに塗布されたグリースが保持される結果、リップの摺動抵抗の低減を図ることができる。これにより低トルク化をより図れる。   As shown in FIG. 2, a plurality of minute recesses 14 may be provided on the sliding surfaces of the grease lip 6, dust lip 5, and side lip (not shown) in the first seal plate 7. Other than the first embodiment, the lip or the like is chlorinated. The roughness of the recess 14 is, for example, Rz = 1 to 8 μm. For example, the grease applied to the lip is held in the recesses 14, so that the sliding resistance of the lip can be reduced. Thereby, the torque can be further reduced.

図３に示すように、２枚のサイドリップ４，４を設けても良い。２枚のサイドリップ４，４は、第２のシール板８における径方向の内外に並ぶ。第１のシール板７の立板部１２における軸受外方側の面には、例えば、多極磁石１５が設けられている。この多極磁石１５は、立板部１２の外径側端、および、軸受内面の外径側端縁付近部にわたって設けられている。多極磁石１５は、円周方向に並ぶ複数の磁極を有する環状の部材である。この多極磁石１５の外向きの面に、図示外の磁気センサが対面配置される。これらにより回転側部材である内輪１の回転を検出する回転検出装置が構成される。
この構成によると、２枚のサイドリップ４，４により耐泥水性の向上を図ることができる。またリップ等に塩素化処理が施されているため、従来技術よりも低トルク化を図れると共に、シール性を確保できる。 As shown in FIG. 3, two side lips 4, 4 may be provided. The two side lips 4, 4 are arranged inside and outside in the radial direction of the second seal plate 8. For example, a multipolar magnet 15 is provided on the surface on the bearing outer side of the standing plate portion 12 of the first seal plate 7. The multipolar magnet 15 is provided over the outer diameter side end of the upright plate portion 12 and the vicinity of the outer diameter side end edge of the bearing inner surface. The multipolar magnet 15 is an annular member having a plurality of magnetic poles arranged in the circumferential direction. A magnetic sensor (not shown) is arranged facing the outward surface of the multipolar magnet 15. These constitute a rotation detection device that detects the rotation of the inner ring 1 that is the rotation-side member.
According to this configuration, the muddy water resistance can be improved by the two side lips 4, 4. Further, since the lip and the like are subjected to chlorination treatment, the torque can be reduced as compared with the prior art, and the sealing performance can be secured.

図４に示すように、リップを３枚のサイドリップ４，ダストリップ５，およびグリースリップ６から成る３リップ構造としても良い。
図５に示すように、リップを２枚のダストリップ５およびグリースリップ６から成る２リップ構造としても良い。
図６に示すように、図１の軸受密封装置における、第１のシール板７の立板部１２に、図３と同様の多極磁石１５を設けてもよい。
いずれかの軸受密封装置において、リップにグリースが塗布され、このリップに塗布するグリースの基油動粘度を、軸受内部に封入するグリースの基油基油動粘度よりも小さくしても良い。この場合、リップの摺動抵抗の低減を図れ、低トルク化をより図れる。前記リップに塗布するグリースの基油動粘度を５ｍｍ２／Ｓ（１００℃）以下としてもよい。 As shown in FIG. 4, the lip may have a three-lip structure including three side lips 4, a dust lip 5, and a grease lip 6.
As shown in FIG. 5, the lip may have a two-lip structure including two dust strips 5 and a grease lip 6.
As shown in FIG. 6, the multipolar magnet 15 similar to FIG. 3 may be provided on the standing plate portion 12 of the first seal plate 7 in the bearing sealing device of FIG. 1.
In any of the bearing sealing devices, grease may be applied to the lip, and the base oil dynamic viscosity of the grease applied to the lip may be smaller than the base oil base oil dynamic viscosity of the grease sealed inside the bearing. In this case, the sliding resistance of the lip can be reduced and the torque can be further reduced. The base oil kinematic viscosity of the grease applied to the lip may be 5 mm 2 / S (100 ° C.) or less.

図７は、いずれかの軸受密封装置を用いた車輪用軸受の断面図である。この車輪用軸受は、第３世代に分類される複列アンギュラ玉軸受型であり、内輪回転タイプで且つ駆動輪支持用のものである。内方部材１Ａ、外方部材２Ａ間に形成される環状空間の両端が、一対の軸受密封装置ＢＲ１，ＢＲ２で密封されている。車両の中央寄りとなるインボード側の軸受密封装置ＢＲ１として、例えば、図１〜図３、図６のいずれかの軸受密封装置が用いられる。車両の車幅方向外側寄りとなるアウトボード側の軸受密封装置ＢＲ２として、例えば、図４の軸受密封装置が用いられる。但し、この例に限定されるものではない。これらの軸受密封装置を用いた車輪用軸受によると、低トルク化とシール性能向上の両立を図れる。シール性能の向上を図れるため、車輪用軸受内部に泥水等が不所望に浸入することを防止しもって軸受寿命を延ばすことができる。なお、いずれかの軸受密封装置を、車輪用軸受以外の軸受に適用しても良い。   FIG. 7 is a cross-sectional view of a wheel bearing using any one of the bearing sealing devices. This wheel bearing is a double-row angular contact ball bearing type classified as the third generation, and is an inner ring rotating type and for driving wheel support. Both ends of the annular space formed between the inner member 1A and the outer member 2A are sealed with a pair of bearing sealing devices BR1 and BR2. As the bearing sealing device BR1 on the inboard side closer to the center of the vehicle, for example, the bearing sealing device of any one of FIGS. 1 to 3 and FIG. 6 is used. For example, the bearing sealing device shown in FIG. 4 is used as the bearing sealing device BR2 on the outboard side that is closer to the outer side in the vehicle width direction of the vehicle. However, it is not limited to this example. According to the wheel bearings using these bearing sealing devices, both reduction in torque and improvement in sealing performance can be achieved. Since the sealing performance can be improved, it is possible to extend the bearing life by preventing muddy water or the like from entering the wheel bearings undesirably. Any one of the bearing sealing devices may be applied to a bearing other than the wheel bearing.

図８は、試験片に対する回転速度と摩擦係数との関係を、塩素化処理の有無で比較して示す図である。例えば２ｍｍの厚みのゴム板から成る試験片を、一般的なサバン型試験機（図示せず）を用いて摩擦係数を評価した。前記サバン型試験機は、試験片の平面に対し、回転するリング状部材の外周面を摺接させる形態である。同図８（１）は、試験片に塩素化処理が施されていないいわゆる「無処理」の試験結果を示す。同図８（２）は、塩素化処理の処理液に試験片を５秒浸漬した試験結果を示し、同図８（３）は、処理液に試験片を６０秒浸漬した試験結果を示す。勿論（１）〜（３）の試験条件は同一とされている。この試験では、例えば、回転速度として、順次40→100→200→400→1000→3000→5000min-1で、各回転数で５分ずつ摩擦係数を測定した。また試験装置の半径などを考慮して図中にプロットする回転速度を変換している。なお、以下に示す各図の試験は、特に記載のない限り、各図において同一の試験条件で行うものとする。
この試験によると、無処理のものに比べ、塩素化処理を施したものは、あらゆる回転速度域において摩擦係数の低減を図れている。 FIG. 8 is a diagram showing the relationship between the rotational speed and the friction coefficient with respect to the test piece, with and without chlorination treatment. For example, the coefficient of friction of a test piece made of a rubber plate having a thickness of 2 mm was evaluated using a general Saban type tester (not shown). The Saban type testing machine is a form in which the outer peripheral surface of the rotating ring-shaped member is in sliding contact with the plane of the test piece. FIG. 8 (1) shows the so-called “no treatment” test result in which the test piece is not subjected to chlorination treatment. FIG. 8 (2) shows the test result of immersing the test piece in the chlorination treatment solution for 5 seconds, and FIG. 8 (3) shows the test result of immersing the test piece in the treatment solution for 60 seconds. Of course, the test conditions (1) to (3) are the same. In this test, for example, as the rotational speed, the friction coefficient was measured for 5 minutes at each rotational speed in the order of 40 → 100 → 200 → 400 → 1000 → 3000 → 5000 min −1 . In addition, the rotational speed plotted in the figure is converted in consideration of the radius of the test apparatus. It should be noted that the tests shown below are performed under the same test conditions in each figure unless otherwise specified.
According to this test, the coefficient of friction of the chlorinated one can be reduced in all rotational speed ranges compared to the non-treated one.

図９は、ゴムの物性変化を測定する測定装置を概略示す図である。
この測定装置では、試験片Ｗに対し、バイブレータ１６により、引張、圧縮荷重を与え、ロードセル１７を介してこの試験片Ｗの粘弾性のパラメータを算出可能になっている。具体的に、ゴムから成る試験片Ｗに、バイブレータ１６により、例えば、周波数１〜１０４Ｈｚの正弦波状の歪みを与える。この場合、ロードセル１７により正弦波状の応力を検出する。この応力は、歪みと同一位相の弾性的成分と、この弾性的成分とは位相が遅れた粘性的成分とに分けられる。これら弾性的成分および粘性的成分から、粘弾性のパラメータとして、例えば、動的貯蔵弾性率、損失正接等を求める。 FIG. 9 is a diagram schematically showing a measuring apparatus for measuring changes in physical properties of rubber.
In this measuring apparatus, tensile and compression loads are applied to the test piece W by the vibrator 16, and viscoelastic parameters of the test piece W can be calculated via the load cell 17. Specifically, for example, a sinusoidal distortion having a frequency of 1 to 10 4 Hz is applied to the test piece W made of rubber by the vibrator 16. In this case, the load cell 17 detects a sinusoidal stress. This stress is divided into an elastic component having the same phase as that of the strain and a viscous component having a phase delayed from the elastic component. From these elastic components and viscous components, for example, dynamic storage elastic modulus, loss tangent and the like are obtained as viscoelastic parameters.

図１０は、ゴムの物性変化を、塩素化処理の有無で比較して示す図である。
同図１０（１）は動的貯蔵弾性率の周波数依存性を示し、同図１０（２）は、損失正接の周波数依存性を示す。これらは、それぞれ図９の測定装置を用い、基準温度２３℃、ニトリルゴムから成る試験片の物性変化を求めた結果である。
図１０（１）に示すように、塩素化処理を施した試験片は、特に軸受回転領域において、無処理のものより、動的貯蔵弾性率が増加し、試験片への負荷に対してつぶれ難くなっている。また図１０（２）に示すように、塩素化処理を施した試験片は、無処理のものより、損失正接が減少し、エネルギーを吸収し難くなっている。なお図１０（１），（２）より、塩素化処理の処理時間の違いによる影響は小さいことが認められた。 FIG. 10 is a diagram showing changes in physical properties of rubber in comparison with the presence or absence of chlorination treatment.
FIG. 10 (1) shows the frequency dependence of the dynamic storage elastic modulus, and FIG. 10 (2) shows the frequency dependence of the loss tangent. These are the results of determining changes in physical properties of a test piece made of nitrile rubber at a reference temperature of 23 ° C. using the measuring device of FIG.
As shown in FIG. 10 (1), the chlorinated test specimen has a larger dynamic storage elastic modulus than the non-treated specimen, particularly in the bearing rotation region, and collapses against the load on the specimen. It has become difficult. Further, as shown in FIG. 10 (2), the test piece subjected to the chlorination treatment has a reduced loss tangent and is less likely to absorb energy than the untreated one. 10 (1) and 10 (2), it was confirmed that the influence due to the difference in the treatment time of the chlorination treatment was small.

図１１は各種の軸受密封装置の回転速度と回転トルクとの関係を示す図である。
軸受に軸受密封装置が組込まれた状態で試験が行われる。軸受密封装置として、例えば、鋼板にシール本体が固着され、このシール本体の内周側端から軸方向内外に二股に分岐して突出するリップを含む形態が適用される。これらリップが、内輪の断面Ｖ字状のシール溝に摺接するようになっている。同図１１（１）は、４個のサンプルを用いた塩素化処理が「無処理」の試験結果を示す。同図１１（２）は、２個のサンプルを用いた石油ベンジンで希釈しない通常の塩素化処理を施した軸受密封装置の試験結果を示し、同図１１（３）は、４個のサンプルを用いた石油ベンジンで希釈した塩素化処理を施した軸受密封装置の試験結果を示す。この試験では、例えば、回転速度として、順次60→120→180→240→300→360→480→600→1800→3600→7200→10000 min-1で回転トルクを測定した。また各図において、サンプル別にマークの種類を変えて表記している。
この試験によると、リップ等を石油ベンジンで希釈した塩素化処理を施すことにより、より低摩擦化を図ることができた。 FIG. 11 is a diagram showing the relationship between the rotational speed and rotational torque of various bearing sealing devices.
The test is performed with the bearing sealing device built into the bearing. As the bearing sealing device, for example, a form in which a seal body is fixed to a steel plate and includes a lip projecting from the inner peripheral side end of the seal body in a bifurcated manner inward and outward in the axial direction is applied. These lips are in sliding contact with a seal groove having a V-shaped cross section of the inner ring. FIG. 11 (1) shows a test result in which the chlorination treatment using four samples is “no treatment”. Fig. 11 (2) shows the test results of a bearing sealing device that was subjected to ordinary chlorination treatment that was not diluted with petroleum benzine using two samples, and Fig. 11 (3) shows four samples. The test result of the bearing sealing apparatus which performed the chlorination process diluted with the used petroleum benzine is shown. In this test, for example, the rotational torque was measured in the order of 60 → 120 → 180 → 240 → 300 → 360 → 480 → 600 → 1800 → 3600 → 7200 → 10000 min −1 as the rotational speed. In each figure, the type of mark is changed for each sample.
According to this test, it was possible to further reduce friction by applying a chlorination treatment in which the lip or the like was diluted with petroleum benzine.

１…内輪
２…外輪
３…シール本体
４…サイドリップ
５…ダストリップ
６…グリースリップ
７…第１のシール板
８…第２のシール板
９，１０…円筒部
１１，１２…立板部
１４…凹部 DESCRIPTION OF SYMBOLS 1 ... Inner ring 2 ... Outer ring 3 ... Seal main body 4 ... Side lip 5 ... Dustrip 6 ... Grease lip 7 ... 1st seal plate 8 ... 2nd seal plate 9, 10 ... Cylindrical part 11, 12 ... Standing plate part 14 ... concave

Claims (9)

軸受の内外輪間の環状空間を密封する軸受密封装置であって、
前記内外輪のいずれか一方に設けられるシール本体と、このシール本体から延び前記内外輪のいずれか他方に接するリップとを有し、このリップの表層に、塩素化された層を有し、当該塩素化された層の表層硬さが同リップの内部硬さよりも高いことを特徴とする軸受密封装置。 A bearing sealing device for sealing an annular space between inner and outer rings of a bearing,
A seal body provided on one of the inner and outer rings, and a lip extending from the seal body and in contact with the other of the inner and outer rings, and having a chlorinated layer on a surface layer of the lip, A bearing sealing device characterized in that the surface hardness of the chlorinated layer is higher than the internal hardness of the lip. 請求項１において、前記塩素化された層が、一酸化二塩素を主成分とし、酢酸エチルを溶媒とした液に非極性溶媒を加えた液に前記リップを浸漬して成る軸受密封装置。   2. The bearing sealing device according to claim 1, wherein the chlorinated layer is formed by immersing the lip in a solution obtained by adding a nonpolar solvent to a solution containing dichlorine monoxide as a main component and ethyl acetate as a solvent. 請求項２において、前記非極性溶媒として石油ベンジンを適用した軸受密封装置。   3. The bearing sealing device according to claim 2, wherein petroleum benzine is applied as the nonpolar solvent. 請求項１ないし請求項３のいずれか１項において、前記液による浸漬で、リップ部に使用するゴム材料（ジエン系）を国際ゴム硬さの単位で２〜５ポイント高くしたことを特徴とする軸受密封装置。   The rubber material (diene type) used for the lip portion is increased by 2 to 5 points in the unit of international rubber hardness by dipping with the liquid according to any one of claims 1 to 3. Bearing sealing device. 請求項１ないし請求項４のいずれか１項において、前記シール本体およびリップがニトリルゴムから成る軸受密封装置。   The bearing sealing device according to any one of claims 1 to 4, wherein the seal body and the lip are made of nitrile rubber. 請求項１ないし請求項５のいずれか１項において、前記軸受として、車輪用軸受が適用される軸受密封装置。   6. The bearing sealing device according to claim 1, wherein a wheel bearing is applied as the bearing. 請求項１ないし請求項６のいずれか１項において、前記軸受密封装置は、前記内外輪のおける回転側部材の周面に嵌合する円筒部およびこの円筒部の端部から立ち上がる立板部を含む断面Ｌ字状の第１のシール板と、
この第１のシール板に対向し、前記内外輪における固定側部材に嵌合される断面Ｌ字状の第２のシール板とを有し、
前記リップは、
前記第２のシール板に固着される前記シール本体から延び、且つ、前記第１のシール板の立板部に摺接するサイドリップと、前記第１のシール板の円筒部に摺接するラジアルリップとを有する軸受密封装置。 7. The bearing sealing device according to claim 1, wherein the bearing sealing device includes a cylindrical portion that fits on a peripheral surface of a rotation side member of the inner and outer rings, and a standing plate portion that rises from an end portion of the cylindrical portion. A first seal plate having an L-shaped cross section including:
A second seal plate facing the first seal plate and having an L-shaped cross section to be fitted to a fixed member in the inner and outer rings,
The lip is
A side lip extending from the seal body fixed to the second seal plate and slidingly contacting the standing plate portion of the first seal plate; and a radial lip slidingly contacting the cylindrical portion of the first seal plate; Bearing sealing device. 請求項６または請求項７において、前記第１のシール板におけるリップの摺動面に、微小な凹部を設けた軸受密封装置。   8. The bearing sealing device according to claim 6, wherein a minute concave portion is provided on a sliding surface of the lip in the first seal plate. 請求項１ないし請求項８のいずれか１項において、前記リップにグリースが塗布され、このリップに塗布するグリースの基油動粘度を、軸受内部に封入するグリースの基油動粘度よりも小さくした軸受密封装置。   9. The grease according to claim 1, wherein grease is applied to the lip, and the base oil kinematic viscosity of the grease applied to the lip is made smaller than the base oil kinematic viscosity of the grease sealed inside the bearing. Bearing sealing device.
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JP2018071604A (en) * 2016-10-26 2018-05-10 Nok株式会社 Sealing device

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JPS6135946A (en) * 1984-07-30 1986-02-20 豊田合成株式会社 Wiper blade rubber
JPH0389202U (en) * 1989-12-27 1991-09-11
JP2006083878A (en) * 2004-09-14 2006-03-30 Nsk Ltd Rolling bearing for wheel
JP2012007663A (en) * 2010-06-24 2012-01-12 Ntn Corp Wheel bearing device

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JPS6135946A (en) * 1984-07-30 1986-02-20 豊田合成株式会社 Wiper blade rubber
JPH0389202U (en) * 1989-12-27 1991-09-11
JP2006083878A (en) * 2004-09-14 2006-03-30 Nsk Ltd Rolling bearing for wheel
JP2012007663A (en) * 2010-06-24 2012-01-12 Ntn Corp Wheel bearing device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018071604A (en) * 2016-10-26 2018-05-10 Nok株式会社 Sealing device

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