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JP4983374B2 - Pack seal rolling bearing - Google Patents

Pack seal rolling bearing Download PDF

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Publication number
JP4983374B2
JP4983374B2 JP2007118026A JP2007118026A JP4983374B2 JP 4983374 B2 JP4983374 B2 JP 4983374B2 JP 2007118026 A JP2007118026 A JP 2007118026A JP 2007118026 A JP2007118026 A JP 2007118026A JP 4983374 B2 JP4983374 B2 JP 4983374B2
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Prior art keywords
cylindrical portion
bearing
slinger
ring
pack seal
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JP2008275038A (en
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勝 橋田
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NSK Ltd
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NSK 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
    • F16C33/7889—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to an inner race and extending toward the outer race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pack seal easy to press and fix without the need for special machining on a bearing and preventive of movement from a fixed position, and to provide the rolling bearing using the same. <P>SOLUTION: The pack seal 1 is formed in a sectional-view L-shape with an annular portion 23 integrally extending from one end 22 of a cylindrical portion 21 fitted to an inner ring outer diameter face 4a of the bearing in the direction of the outer diameter. It comprises a core metal 2 having at least one lip 2a formed by integrally vulcanizing and molding an elastic body, and a slinger 3 consisting of a cylindrical portion 31 opposed to the cylindrical portion of the core metal and fitted to an outer ring inner diameter face 5a of the bearing, and a first annular portion 33 integrally extending from one end 32 of the cylindrical portion in the direction of the inner diameter and opposed to the annular portion of the core metal. A second annular portion 35 integrally extends from the other end 34 of the cylindrical portion of the slinger in the direction of the outer diameter. The cylindrical portion is fitted to the inner peripheral face of the outer ring of the rolling bearing, and the second annular portion is fitted to the end face of the outer ring. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

本発明は、軸受に特別な加工を行うことなく容易に圧入可能、かつ、圧入後に適正位置から移動することを防止したパックシールに関する。   The present invention relates to a pack seal that can be easily press-fitted without any special processing on a bearing and that prevents movement from an appropriate position after press-fitting.

従来から、例えば、図４及び図５に示すように、パックシール１は、芯金２と、該芯金２に一体に備えられたリップ２ａと、スリンガーとからなり、芯金２は、転がり軸受の外輪５の内径面と嵌合する円筒部２１と、該円筒部２１の一端２２から内径方向に円環部２３を一体に延設して断面視Ｌ字型に構成されている。スリンガー３は、前記芯金２の円筒部２１と対向して、転がり軸受の内輪４の外径面と嵌合する円筒部３１と、該円筒部３１の一端３２から外径方向に一体に延設され、前記芯金２の円環部２３と対向する円環部３３とで断面Ｌ字型に構成されている。その芯金２やスリンガー３は、一般的に、防食鋼または防食処理された鋼をプレス成形して薄肉に形成されている。リップ２ａは、該芯金２にシールゴムを一体に加硫して成形し、通常、１つ以上のリップが設けられるとともに、前記スリンガー３と摺接している。
このようなパックシール１は、その断面が小さい割に軸受内部を密封する性能が高いため、パックシール１を配する領域が比較的狭い転がり軸受に好適に用いられ、特に厳しい泥水が降りかかるような悪条件下で稼動するハブユニット軸受の軸受内部を密封する用途に用いられている。 Conventionally, for example, as shown in FIGS. 4 and 5, the pack seal 1 includes a cored bar 2, a lip 2 a provided integrally with the cored bar 2, and a slinger, and the cored bar 2 is rolled. A cylindrical portion 21 fitted to the inner diameter surface of the outer ring 5 of the bearing and an annular portion 23 extending integrally from the one end 22 of the cylindrical portion 21 in the inner diameter direction are configured in an L shape in cross section. The slinger 3 is opposed to the cylindrical portion 21 of the core metal 2 and extends integrally from the cylindrical portion 31 fitted to the outer diameter surface of the inner ring 4 of the rolling bearing and the one end 32 of the cylindrical portion 31 in the outer diameter direction. The annular part 23 of the cored bar 2 and the annular part 33 opposed to each other are formed in an L-shaped cross section. The cored bar 2 and slinger 3 are generally formed thin by press-molding anticorrosive steel or anticorrosive steel. The lip 2 a is formed by integrally vulcanizing a seal rubber on the core metal 2, and usually one or more lips are provided and are in sliding contact with the slinger 3.
Such a pack seal 1 has a high performance for sealing the inside of the bearing even though its cross section is small. Therefore, the pack seal 1 is preferably used for a rolling bearing having a relatively narrow region where the pack seal 1 is disposed, and particularly severe mud falls. It is used for sealing the inside of a hub unit bearing that operates under adverse conditions.

ハブユニット軸受は、自動車の車輪Ｗ（例えば、ディスクホイール）を車体Ｂ（例えば、懸架装置（サスペンション））に対して回転自在に支持するための転がり軸受であり、例えば図４に示すように、車体Ｂ側に固定されて常時非回転状態に維持される静止輪（例えば外輪）５と、外輪５の内側に対向して設けられ且つ車輪側に接続されて車輪と共に回転する回転輪（例えば内輪）４と、外輪５と内輪４との間に複列（例えば２列）で回転可能に組み込まれた複数の転動体６，７とを備えている。この場合、外輪５は中空円筒状を成しており、内輪４の外周を覆うように配置されている。なお、転動体６，７として図面では、玉を例示しているが、軸受ユニットの構成や種類に応じて、コロが適用される場合もある。   The hub unit bearing is a rolling bearing for rotatably supporting a vehicle wheel W (for example, a disc wheel) with respect to a vehicle body B (for example, a suspension device (suspension)). For example, as shown in FIG. A stationary wheel (for example, an outer ring) 5 that is fixed to the vehicle body B side and is maintained in a non-rotating state at all times, and a rotating wheel (for example, an inner ring) that is provided facing the inner side of the outer ring 5 and that is connected to the wheel side and rotates with the wheel. ) 4 and a plurality of rolling elements 6 and 7 rotatably incorporated in a double row (for example, two rows) between the outer ring 5 and the inner ring 4. In this case, the outer ring 5 has a hollow cylindrical shape and is arranged so as to cover the outer periphery of the inner ring 4. In addition, although the ball | bowl is illustrated in drawing as the rolling elements 6 and 7, a roller may be applied according to the structure and kind of bearing unit.

また、内輪４には、例えば自動車のディスクホイールＷを支持しつつ共に回転する略円筒形状のハブ８が設けられており、ハブ８には、外輪５を越えて外方（ハブ８の半径方向外側）に向って延出するとともに、ディスクホイールＷが固定されるハブフランジ８ａが突設されている。なお、ハブフランジ８ａは、その延出縁付近に、周方向に沿って所定間隔で配置された複数のハブボルト１０を備え、該ハブボルト１０によって、ディスクホイールＷがハブフランジ８ａに対して位置決めして固定される。   Further, the inner ring 4 is provided with a substantially cylindrical hub 8 that rotates together with, for example, a disc wheel W of an automobile, and the hub 8 extends beyond the outer ring 5 outward (in the radial direction of the hub 8). A hub flange 8a is provided so as to extend outward) and to which the disc wheel W is fixed. The hub flange 8a includes a plurality of hub bolts 10 arranged at predetermined intervals along the circumferential direction in the vicinity of the extending edge thereof, and the hub wheel 10 positions the disc wheel W with respect to the hub flange 8a. Fixed.

さらに、ハブ８には、車体側に環状の回転輪構成体９（ハブ８と共に回転輪４を構成する部材）が嵌合（外嵌）されるようになっている。このとき、軸受ユニットには所定の予圧が付与された状態となり、この状態において、各転動体６，７は、互いに所定の接触角を成して内輪４と外輪５の軌道面（静止軌道面５ｓ、回転軌道面４ｓ）にそれぞれ接触して回転可能に組み込まれる。
また、内輪４と外輪５との間であって、転動体６の車輪Ｗ側には、外輪５に内嵌された芯金からハブ８に摺接するリップシール１１が設けられる。
さらに、内輪４と外輪５との間であって、転動体７の車体Ｂ側には、前記パックシール１が嵌合して配されている。
前記リップシール１１とパックシール１によって、軸受の内部を密封して、軸受の外部から降りかかる泥水等が軸受の内部に侵入することを防止している。 Further, an annular rotating wheel structure 9 (a member constituting the rotating wheel 4 together with the hub 8) is fitted (externally fitted) to the hub 8 on the vehicle body side. At this time, a predetermined preload is applied to the bearing unit, and in this state, the rolling elements 6 and 7 form a raceway surface (stationary raceway surface) of the inner ring 4 and the outer ring 5 with a predetermined contact angle with each other. 5s and the rotating raceway surface 4s) are in contact with each other and are rotatably incorporated.
Further, a lip seal 11 is provided between the inner ring 4 and the outer ring 5 and on the wheel W side of the rolling element 6 so as to be in sliding contact with the hub 8 from a core metal fitted in the outer ring 5.
Further, the pack seal 1 is fitted and disposed between the inner ring 4 and the outer ring 5 on the vehicle body B side of the rolling element 7.
The lip seal 11 and the pack seal 1 seal the inside of the bearing and prevent muddy water or the like falling from the outside of the bearing from entering the inside of the bearing.

ところで、ハブユニット軸受は、加工上およびコストの問題から、一般的に、内輪４の外径面４ａ又は、外輪５の内径面５ａの寸法の公差幅は概ね０．１ｍｍであり、これにハウジングや軸の寸法の公差も合わせて考慮すると、ハブユニット軸受のパックシール１が嵌合する嵌合代には、大きなばらつきがでてしまう。
一方、スリンガー３や芯金２は、一般的に、防食鋼または防食処理された鋼をプレス成形して薄肉に形成するため、前記嵌合代が過大になった場合には、パックシール１を大きな力で圧入することとなり、スリンガー３の円環部３３や芯金２の円環部２３がテーパー状に変形してしまう場合がある（例えば、図５中、スリンガー３の破線３３ａ，３３ｂ参照）。その場合、変形の方向によって、リップ２ａとスリンガー３の締め代が増減して、適正な締め代とはならず、シールの防水性能に悪影響が生じる虞がある。
By the way, the hub unit bearing generally has a tolerance width of the outer diameter surface 4a of the inner ring 4 or the inner diameter surface 5a of the outer ring 5 is approximately 0.1 mm due to processing and cost problems. If the tolerances of the shaft and the dimensions of the shaft are taken into account, the fitting allowance for fitting the pack seal 1 of the hub unit bearing will vary greatly.
On the other hand, the slinger 3 and the cored bar 2 are generally formed by press-molding anticorrosion steel or steel subjected to anticorrosion treatment to form a thin wall. Therefore, when the fitting allowance is excessive, the pack seal 1 is removed. The ring portion 33 of the slinger 3 and the ring portion 23 of the core metal 2 may be deformed into a taper shape (see, for example, broken lines 33a and 33b of the slinger 3 in FIG. 5). ). In that case, depending on the direction of deformation, the tightening allowance of the lip 2a and the slinger 3 may increase or decrease, and the proper tightening allowance may not be achieved, which may adversely affect the waterproof performance of the seal.

そこで、従来は、リップ２ａとスリンガー３の締め代の限界値となるように最大嵌合代を決定するとともに、該最大嵌合代から、上記軸受加工の際に生じる加工公差を差し引いて、最小の嵌合代を決定することが多い。ところが、最小嵌合代にあわせて軸受を加工した場合には、嵌合によるパックシール１を固定する力が弱く、パックシール１に想定外の大きな力が加わった場合には、スリンガー３や芯金２が移動してしまったり変形してしまったりする場合もある。また、転がり軸受の内輪４及び外輪５は、転動体６，７の通過によって微少に変形するので、最小嵌合代でパックシール１が取り付けられた場合には、該変形によって、パックシール１にクリープ（正常方向とは逆の回転が生じる現象）が発生し、スリンガー３や芯金２が移動してしまう場合もある。   Therefore, conventionally, the maximum fitting allowance is determined so as to be the limit value of the fastening allowance between the lip 2a and the slinger 3, and the machining tolerance generated during the above-mentioned bearing machining is subtracted from the maximum fitting allowance to obtain the minimum The mating allowance is often determined. However, when the bearing is processed in accordance with the minimum fitting allowance, the force for fixing the pack seal 1 by fitting is weak, and when a large unexpected force is applied to the pack seal 1, the slinger 3 or the core The gold 2 may move or be deformed. Further, since the inner ring 4 and the outer ring 5 of the rolling bearing are slightly deformed by the passage of the rolling elements 6, 7, when the pack seal 1 is attached with the minimum fitting allowance, the deformation causes the pack seal 1 to be deformed. Creep (a phenomenon in which rotation opposite to the normal direction occurs) occurs, and the slinger 3 and the cored bar 2 may move.

このように、パックシール１のスリンガー３や芯金２が移動すると、リップ２ａとスリンガー３の締め代が適正な締め代ではなくなり、パックシール１の防水性能が低下して転がり軸受に水が浸入して、フレーキング（軸受の転動面がうろこ状に剥がれる現象）が発生して転がり軸受が破損する虞もあり、または、動いたスリンガー３や芯金２が転動体７と接触して噛み込みが発生し、軸受がロックするに至って激しい損傷となる虞もある。また、パックシール１の移動は、転がり軸受に負荷されるモーメント荷重の影響もあって、軸受内部方向に移動することが多い。   As described above, when the slinger 3 or the core metal 2 of the pack seal 1 moves, the tightening margin of the lip 2a and the slinger 3 is not an appropriate tightening margin, and the waterproof performance of the pack seal 1 is lowered and water enters the rolling bearing. In addition, flaking (a phenomenon in which the rolling surface of the bearing peels off in a scaly manner) may occur and the rolling bearing may be damaged, or the slinger 3 or the core metal 2 that has moved contacts the rolling element 7 and bites. There is also a risk that the bearing may lock up and cause severe damage. Further, the movement of the pack seal 1 is often moved in the direction toward the inside of the bearing due to the influence of the moment load applied to the rolling bearing.

そこで、スリンガー３や芯金２が軸受内部方向に移動することを防止する技術が望まれる。例えば、特許文献１は、予め軸受に形成しておいた段部に芯金を嵌合する技術を開示している。
しかし、特許文献１では、軸受に、予め段部を形成する必要があるため、その加工のための費用とコストが増加するとともに、パックシールの圧入に特別な技術を要するなどの問題がある。 Therefore, a technique for preventing the slinger 3 and the cored bar 2 from moving in the bearing inner direction is desired. For example, patent document 1 is disclosing the technique which fits a metal core to the step part previously formed in the bearing.
However, in patent document 1, since it is necessary to form a step part in a bearing beforehand, the expense and cost for the process increase, and there exists a problem that a special technique is required for press-fitting of a pack seal.

実用新案登録第２５２９９５６号公報Utility Model Registration No. 2529956

本発明は、上記の問題を解決するためになされており、その目的は、軸受に特別の加工を行うことなく圧入固定が容易で、固定位置から移動することを防止したパックシールを提供し、そのパックシールを適用した転がり軸受を提供することである。   The present invention has been made in order to solve the above-mentioned problems, and its purpose is to provide a pack seal that is easy to press-fit without performing special processing on the bearing, and prevents movement from a fixed position. It is to provide a rolling bearing to which the pack seal is applied.

上記課題を達成するために、本発明は、転がり軸受の内輪の外径面に直接嵌合する円筒部の軸受外部側の一端から外径方向に円環部を一体に延設して断面視Ｌ字型に構成され、弾性体を一体に加硫成形して１つ以上のリップを備えた芯金と、前記芯金の円筒部と対向して、転がり軸受の外輪の内径面と嵌合する円筒部と、該円筒部の軸受内部側の一端から内径方向に一体に延設され、前記芯金の円環部と対向する第一の円環部とで構成されたスリンガーとからなり、前記リップがスリンガーに摺動するパックシールにおいて、スリンガーの円筒部の軸受外部側の他端から第二の円環部が外径方向に一体に延設され、第二の円環部は該外輪の端面と当接し、スリンガーの第一の円環部は、芯金の円筒部の軸受内部側の遊端よりも軸受内部方向に位置するとともに、スリンガーの第一の円環部の遊端の内径寸法は、芯金の円筒部の遊端の外径寸法よりも小径となるように設定されている。また、前記芯金の円筒部は、転がり軸受の内輪の外径面と嵌合する第一の円筒部と、該第一の円筒部から、段差を有して前記第一の円筒部よりも大径に延設された第二の円筒部からなり、スリンガーの第一の円環部の遊端は、芯金の円筒部の遊端側よりも軸受内部方向に位置し、芯金の第二の円筒部の遊端の外径寸法は、スリンガーの第一の円環部の遊端の内径寸法よりも大径となるように設定されている場合もある。さらに、前記第二の円筒部の遊端の内径側には弾性部材が一体に配され、内輪外径面との間にシールを構成している場合もある。また、上述のパックシールを適用した転がり軸受としても良い。 In order to achieve the above object, the present invention provides a circular ring portion integrally extending in the outer diameter direction from one end on the bearing outer side of a cylindrical portion that is directly fitted to the outer diameter surface of the inner ring of a rolling bearing. Constructed in an L-shape, an elastic body is integrally vulcanized and formed with a core bar having one or more lips, and is fitted to the inner surface of the outer ring of the rolling bearing facing the cylindrical portion of the core bar And a slinger composed of a first annular portion that is integrally extended in the inner diameter direction from one end on the bearing inner side of the cylindrical portion, and that faces the annular portion of the metal core, In the pack seal in which the lip slides on the slinger, the second annular portion is integrally extended in the outer diameter direction from the other end of the cylindrical portion of the slinger on the outside of the bearing , and the second annular portion is the outer ring. The first ring portion of the slinger is in contact with the inner end of the cylindrical portion of the cored bar in the bearing inner direction than the free end of the inner side of the bearing. As well as location, the inner diameter of the free end of the first annular portion of the slinger is set to be smaller than the outer diameter of the free end of the cylindrical portion of the metal core. Further, the cylindrical portion of the metal core has a first cylindrical portion fitted to the outer diameter surface of the inner ring of the rolling bearing, and has a step from the first cylindrical portion, than the first cylindrical portion. The free end of the first annular part of the slinger is located in the bearing inner direction from the free end side of the cylindrical part of the core metal, The outer diameter dimension of the free end of the second cylindrical part may be set to be larger than the inner diameter dimension of the free end of the first annular part of the slinger. Furthermore, an elastic member may be integrally provided on the inner diameter side of the free end of the second cylindrical portion, and a seal may be formed between the inner ring and the outer diameter surface. Moreover, it is good also as a rolling bearing which applied the above-mentioned pack seal.

本発明によれば、軸受に特別の加工を行うことなく圧入固定が容易で、固定位置から移動することを防止したパックシールを提供し、そのパックシールを適用した転がり軸受を提供することができる。   According to the present invention, it is possible to provide a pack seal that can be easily press-fitted and fixed without performing any special processing on the bearing and prevent the bearing from moving from the fixed position, and to provide a rolling bearing to which the pack seal is applied. .

以下、本発明の一実施の形態に係るパックシール１について、添付図面に基づいて説明する。なお、パックシール１は、上述した従来の転がり軸受の軸受内部を密封する目的で使用されるものであり、例えば、ハブユニット軸受の静止輪５と回転輪４との間であって、転動体７の車体Ｂ側には、前記パックシール１が嵌合して配される。   Hereinafter, pack seal 1 concerning one embodiment of the present invention is explained based on an accompanying drawing. The pack seal 1 is used for the purpose of sealing the inside of the conventional rolling bearing described above. For example, between the stationary ring 5 and the rotating ring 4 of the hub unit bearing, the pack seal 1 is a rolling element. 7, the pack seal 1 is fitted and arranged on the vehicle body B side.

パックシール１は、芯金２と、芯金２の外径側に配されたスリンガー３と、該スリンガー３と摺接し、芯金２と一体に形成されたリップ２ａとからなる。
芯金２は、転がり軸受、例えば、ハブユニット軸受の内輪の外径面と嵌合する円筒部２１の一端２２から外径方向に円環部２３を一体に延設して断面視Ｌ字型に構成されている。
スリンガー３は、前記芯金２の円筒部と対向して、転がり軸受の外輪の内径面と嵌合する円筒部３１と、該円筒部３１の一端３２から内径方向に一体に延設され、前記芯金２の円環部２３と対向する第一の円環部３３が延設されるとともに、円筒部３１の他端３４からは、外径方向に第二の円環部３５を延設して、断面視クランク型に構成されている。
なお、スリンガー３の第一の円環部３３の遊端３３ａの内径寸法Ｄ１は、芯金２の円筒部２１の遊端２１ａ側よりも軸受内部方向に位置するとともに、その芯金２の円筒部２１の遊端２１ａの外径寸法Ｄ２よりも小径となるように設定されている。 The pack seal 1 includes a metal core 2, a slinger 3 disposed on the outer diameter side of the metal core 2, and a lip 2 a that is in sliding contact with the slinger 3 and formed integrally with the metal core 2.
The cored bar 2 is an L-shaped cross-sectional view in which a ring portion 23 is integrally extended in an outer diameter direction from one end 22 of a cylindrical portion 21 that is fitted to an outer diameter surface of a rolling bearing, for example, an inner ring of a hub unit bearing. It is configured.
The slinger 3 is opposed to the cylindrical portion of the core metal 2 and is integrally extended in the inner diameter direction from a cylindrical portion 31 fitted to the inner diameter surface of the outer ring of the rolling bearing, and one end 32 of the cylindrical portion 31. A first annular portion 33 facing the annular portion 23 of the core metal 2 is extended, and a second annular portion 35 is extended from the other end 34 of the cylindrical portion 31 in the outer diameter direction. Thus, it is configured as a crank type in sectional view.
The inner diameter D1 of the free end 33a of the first annular portion 33 of the slinger 3 is located in the bearing inner direction from the free end 21a side of the cylindrical portion 21 of the core metal 2, and the cylinder of the core metal 2 The diameter is set to be smaller than the outer diameter D2 of the free end 21a of the portion 21.

リップ２ａは、前記芯金２の内側面と一体に弾性体が加硫成形され、少なくとも一つ以上形成されるとともに、前記スリンガー３と摺接している。本実施形態では、リップ２ａとして、芯金２の円環部２３の遊端側から延設されるとともにスリンガー３の円筒部３１と摺接する第一リップ２ｂと、芯金２の円環部２３の遊端側から延設されるとともにスリンガー３の第一の円環部３３と摺接する第二リップ２ｃと、芯金２の円筒部２１の遊端側から延設されるとともにスリンガー３の第一の円環部３３と摺接する第三リップ２ｄを備えている。   The lip 2 a is formed by vulcanizing an elastic body integrally with the inner surface of the core metal 2, and at least one lip 2 a is formed, and is in sliding contact with the slinger 3. In the present embodiment, as the lip 2 a, a first lip 2 b that extends from the free end side of the annular portion 23 of the core metal 2 and slidably contacts the cylindrical portion 31 of the slinger 3, and the annular portion 23 of the core metal 2. The second lip 2c extending from the free end side of the slinger 3 and in sliding contact with the first annular portion 33 of the slinger 3, and the second lip 2c extending from the free end side of the cylindrical portion 21 of the core metal 2 and A third lip 2d that is in sliding contact with one annular portion 33 is provided.

第一リップ２ｂは軸受外方（図中の右向き矢印方向）に向けて摺接し、第二リップ２ｃ及び第三リップ２ｄは、スリンガー３の円筒部３１の方向に向けて摺接している。すなわち、各リップとも、軸受外方からの泥水等が軸受内部に侵入しないように密封するダストシールとしての役割を持たされている。
なお、リップ２ａが加硫成形される材料として、本実施形態では、ニトリルゴムやアクリルゴム等の弾性材が使用される。なお、リップを形成する材料は、これに限定されず、スリンガー３と摺接して軸受の内部を密封することができれば、どのような材料で形成されていても良い。例えば、ゴムやプラスチックや合成樹脂等で形成されていても良い。 The first lip 2b is in sliding contact with the bearing outward (in the direction of the rightward arrow in the figure), and the second lip 2c and the third lip 2d are in sliding contact with the cylindrical portion 31 of the slinger 3. That is, each lip has a role as a dust seal for sealing so that muddy water or the like from the outside of the bearing does not enter the inside of the bearing.
In this embodiment, an elastic material such as nitrile rubber or acrylic rubber is used as a material for vulcanization molding of the lip 2a. The material for forming the lip is not limited to this, and any material may be used as long as it can slide in contact with the slinger 3 and seal the inside of the bearing. For example, it may be formed of rubber, plastic, synthetic resin, or the like.

このように形成されたパックシール１をハブユニット軸受に嵌合する場合には、まず、芯金２の円筒部２１が内輪４の外径面４ａと嵌合し、スリンガー３の円筒部３１が外輪５の内径面５ａと嵌合する。このとき、芯金２の円環部２３に加えてスリンガー３の第二の円環部３５が圧入時の力を受け止めるので、芯金２やスリンガー３が変形することがない。
さらに、パックシール１をハブユニット軸受内部方向（図中、左向き矢印方向）に押し込むと、スリンガー３の第二の円環部３５が、外輪５の端面５ｂに当接して、当接した位置より内部方向への移動が抑制される。これにより、スリンガー３がハブユニット軸受に対して軸方向に位置決めされるので、ハブユニット軸受が最小嵌合代にあわせて加工され、嵌合によるパックシール１を固定する力が比較的弱い場合であっても、パックシール１は、軸受内部方向に移動することがなく、常に、正常な嵌合位置に固定される。すなわち、パックシール１のリップ２ａ（第一リップ２ｂ，第二リップ２ｃ，第三リップ２ｄ）は、常に、正常な締め代を保つことができ、パックシール１の防水性能が確保される。 When the pack seal 1 thus formed is fitted to the hub unit bearing, first, the cylindrical portion 21 of the core metal 2 is fitted to the outer diameter surface 4a of the inner ring 4, and the cylindrical portion 31 of the slinger 3 is The outer ring 5 is fitted with the inner diameter surface 5a. At this time, since the second annular portion 35 of the slinger 3 receives the force at the time of press-fitting in addition to the annular portion 23 of the core metal 2, the core metal 2 and the slinger 3 are not deformed.
Further, when the pack seal 1 is pushed in the hub unit bearing inward direction (left arrow direction in the figure), the second annular portion 35 of the slinger 3 comes into contact with the end surface 5b of the outer ring 5, and from the contacted position. Movement in the internal direction is suppressed. Thereby, since the slinger 3 is positioned in the axial direction with respect to the hub unit bearing, the hub unit bearing is processed in accordance with the minimum fitting allowance, and the force for fixing the pack seal 1 by fitting is relatively weak. Even if it exists, the pack seal | sticker 1 does not move to a bearing inside direction, but is always fixed to a normal fitting position. That is, the lip 2a (first lip 2b, second lip 2c, third lip 2d) of the pack seal 1 can always maintain a normal tightening margin, and the waterproof performance of the pack seal 1 is ensured.

また、スリンガー３の第一の円環部３３の遊端３３ａの内径寸法Ｄ１は、芯金２の円筒部２１の遊端２１ａ側よりも軸受内部方向に位置するとともに、その芯金２の円筒部２１の遊端２１ａの外径寸法Ｄ２よりも小径となるように設定されているので、万一、芯金２が軸受内部方向に移動してしまった場合であっても、芯金２の円筒部２１の遊端２１ａが、軸方向に位置決めされているスリンガー３の第一の円環部３３の遊端３３ａに当接する。これにより、芯金２は、当接した位置より軸受内部方向への移動が抑制される。従って、スリンガー３や芯金２が転動体７に噛み込まれることが防止されて、ロックによる激しい損傷からハブユニット軸受を護ることができる。
さらに、軸受外方からの泥水等が軸受内部に侵入しないように密封するための複数のダストシールを無理なく成形できるため、耐泥水性能の優れたパックシールを設計することができる。 In addition, the inner diameter D1 of the free end 33a of the first annular portion 33 of the slinger 3 is located closer to the bearing inside than the free end 21a side of the cylindrical portion 21 of the core metal 2, and the cylinder of the core metal 2 Since the diameter is set to be smaller than the outer diameter D2 of the free end 21a of the portion 21, even if the core metal 2 has moved in the bearing inner direction, The free end 21 a of the cylindrical portion 21 abuts on the free end 33 a of the first annular portion 33 of the slinger 3 that is positioned in the axial direction. Thereby, the metal core 2 is restrained from moving in the bearing internal direction from the contacted position. Therefore, the slinger 3 and the cored bar 2 are prevented from being bitten by the rolling elements 7, and the hub unit bearing can be protected from severe damage caused by the lock.
Furthermore, since a plurality of dust seals for sealing so that muddy water from the outside of the bearing does not enter the inside of the bearing can be formed without difficulty, a pack seal having excellent muddy water resistance can be designed.

本実施例では、芯金２の円筒部２１の形状に特徴を有する。パックシール１のその他の構成や作用効果は上述した実施例１と同様であるので、同一の符号を用いることでその説明を省略し、ここでは、本実施例２の特徴部分を中心に説明する。
本実施例２による芯金２の円筒部２１は、図２に示すように、転がり軸受の内輪４の外径面４ａと嵌合する第一の円筒部２４と、該第一の円筒部２４から、段差を有して前記第一の円筒部２４よりも大径に延設された第二の円筒部２５とで構成されている。
また、スリンガー３の第一の円環部３３の遊端３３ａは、芯金２の円筒部２１の遊端２１ａ側よりも軸受内部方向に位置し、芯金２の第二の円筒部２５の遊端２１ａ（円筒部２１の遊端）の外径寸法Ｄ３は、スリンガー３の第一の円環部３３の遊端３３ａの内径寸法Ｄ１よりも大径となるように設定されている。 This embodiment is characterized by the shape of the cylindrical portion 21 of the core 2. Since the other configurations and operational effects of the pack seal 1 are the same as those of the first embodiment described above, the description thereof is omitted by using the same reference numerals, and here, the description will focus on the features of the second embodiment. .
As shown in FIG. 2, the cylindrical portion 21 of the metal core 2 according to the second embodiment includes a first cylindrical portion 24 that is fitted to the outer diameter surface 4 a of the inner ring 4 of the rolling bearing, and the first cylindrical portion 24. And a second cylindrical portion 25 having a step and extending larger in diameter than the first cylindrical portion 24.
Further, the free end 33 a of the first annular portion 33 of the slinger 3 is located closer to the bearing inside than the free end 21 a side of the cylindrical portion 21 of the core metal 2, and the second cylindrical portion 25 of the core metal 2 The outer diameter D3 of the free end 21a (the free end of the cylindrical portion 21) is set to be larger than the inner diameter D1 of the free end 33a of the first annular portion 33 of the slinger 3.

芯金２の円筒部２１をこのように形成した場合であっても、前述した実施例１と同様に、万一、芯金２が軸受内部方向に移動してしまった場合であっても、芯金２の第二の円筒部２５の遊端２１ａが、軸方向に位置決めされているスリンガー３の第一の円環部３３の遊端３３ａに当接する。これにより、芯金２の内部方向への移動の抑制されるので、ハブユニット軸受を激しい損傷から護ることができる。   Even when the cylindrical portion 21 of the cored bar 2 is formed in this way, as in the case of the first embodiment, even if the cored bar 2 has moved in the bearing inner direction, The free end 21a of the second cylindrical portion 25 of the core metal 2 abuts on the free end 33a of the first annular portion 33 of the slinger 3 positioned in the axial direction. Thereby, since the movement to the internal direction of the metal core 2 is suppressed, the hub unit bearing can be protected from severe damage.

本実施例では、前述した実施例２に加えて、図３に示すように、芯金２の第二の円筒部２５の遊端２１ａの内径側２６に弾性体２ｅが一体に配されていることに特徴を有する。本変形例２のその他の構成及び作用効果は、上述した実施例１及び実施例２と同様であるので、同一の符号を用いることでその説明を省略し、ここでは、本実施例３の特徴部分を中心に説明する。
芯金２の第二の円筒部２５の遊端２１ａの内径側２６には、芯金２の内側面と一体に弾性体２ｅが加硫成形されて配されている。この場合において、該弾性体２ｅは、リップ２ａと連続して該遊端２１ａの内径側２６を被覆するとともに、内輪外径面との間にシールを構成している。 In this embodiment, in addition to the second embodiment described above, as shown in FIG. 3, the elastic body 2 e is integrally disposed on the inner diameter side 26 of the free end 21 a of the second cylindrical portion 25 of the core metal 2. It has a special feature. Other configurations and operational effects of the second modification are the same as those of the first and second embodiments described above, and therefore the description thereof is omitted by using the same reference numerals. Here, the features of the third embodiment are described. The explanation will focus on the part.
On the inner diameter side 26 of the free end 21 a of the second cylindrical portion 25 of the core metal 2, an elastic body 2 e is vulcanized and integrated with the inner surface of the core metal 2. In this case, the elastic body 2e covers the inner diameter side 26 of the free end 21a continuously with the lip 2a and forms a seal with the inner ring outer diameter surface.

このように弾性体２ｅを前記遊端２１ａの内径側２６に配することによって、パックシール１をハブユニット軸受に嵌合した場合には、芯金２の円筒部２１と、回転輪（内輪）４の外径面４ａとの嵌合面が弾性体２ｅによってシールされることとなる。従って、万一、回転輪（内輪）４の外径面４ａとの嵌合面を伝って泥水等が浸入してきた場合であっても、侵入してきた泥水等を弾性体２ｅが堰き止め、泥水等が弾性体２ｅの位置よりも軸受内部方向へ侵入することを抑制して、ハブユニット軸受の内部を密封することができる。   By arranging the elastic body 2e on the inner diameter side 26 of the free end 21a in this way, when the pack seal 1 is fitted to the hub unit bearing, the cylindrical portion 21 of the core metal 2 and the rotating ring (inner ring) 4, the fitting surface with the outer diameter surface 4a is sealed by the elastic body 2e. Accordingly, even if muddy water or the like has entered through the fitting surface with the outer diameter surface 4a of the rotating wheel (inner ring) 4, the elastic body 2e blocks the muddy water or the like that has entered the muddy water. It is possible to seal the inside of the hub unit bearing by suppressing the intrusion of etc. from the position of the elastic body 2e toward the inside of the bearing.

上述した各実施例では、パックシール１に配されるリップ２ａとして、第一リップ２ｂ，第二リップ２ｃ，第三リップ２ｄの３つのリップを配した場合を説明したが、リップ２ａは１つ以上配されていれば良いので、その数は特に限定されない。また、リップ２ａはダストシールに限られず、複数のリップの一部がオイルシールを構成していても良い。
また、上述の各実施例では、パックシール１をハブユニット軸受に適用したが、これに限定されず、軸受内部の密封を要する転がり軸受であれば、他の転がり軸受に適用することも本発明の範囲内である。 In each of the above-described embodiments, the case where three lips of the first lip 2b, the second lip 2c, and the third lip 2d are disposed as the lip 2a disposed on the pack seal 1 has been described. The number is not particularly limited as long as it is arranged as described above. The lip 2a is not limited to a dust seal, and some of the lips may constitute an oil seal.
Further, in each of the above-described embodiments, the pack seal 1 is applied to the hub unit bearing. However, the present invention is not limited to this, and the present invention can be applied to other rolling bearings as long as it is a rolling bearing that requires sealing inside the bearing. Is within the range.

本発明によるパックシールの第一実施例を示す断面図である。It is sectional drawing which shows the 1st Example of the pack seal by this invention. 本発明によるパックシールの第二実施例を示す断面図である。It is sectional drawing which shows the 2nd Example of the pack seal by this invention. 本発明によるパックシールの第三実施例を示す断面図である。It is sectional drawing which shows the 3rd Example of the pack seal by this invention. パックシールが適用されるハブユニット軸受の構成を説明する断面図である。It is sectional drawing explaining the structure of the hub unit bearing to which a pack seal is applied. 従来のパックシールの構成を説明する断面図である。It is sectional drawing explaining the structure of the conventional pack seal.

符号の説明Explanation of symbols

２ 芯金
２ａ リップ
３ スリンガー
２１ 芯金の円筒部
２２ 芯金の円筒部の一端
２３ 芯金の円環部
３１ スリンガーの円筒部
３２ スリンガーの円筒部の一端
３３ スリンガーの第一の円環部
３４ スリンガーの円筒部の他端
３５ スリンガーの第二の円環部 2 Core metal 2 a Lip 3 Slinger 21 Cylindrical part 22 of the core metal 23 One end 23 of the cylindrical part of the core metal 31 Circular part of the core metal 31 Cylindrical part 32 of the slinger 33 First cylindrical part 34 of the slinger The other end 35 of the cylindrical part of the slinger The second annular part of the slinger

Claims (4)

転がり軸受の内輪の外径面に直接嵌合する円筒部の軸受外部側の一端から外径方向に円環部を一体に延設して断面視Ｌ字型に構成され、弾性体を一体に加硫成形して１つ以上のリップを備えた芯金と、
前記芯金の円筒部と対向して、転がり軸受の外輪の内径面と嵌合する円筒部と、該円筒部の軸受内部側の一端から内径方向に一体に延設され、前記芯金の円環部と対向する第一の円環部とで構成されたスリンガーとからなり、前記リップがスリンガーに摺動するパックシールにおいて、
スリンガーの円筒部の軸受外部側の他端から第二の円環部が外径方向に一体に延設され、第二の円環部は該外輪の端面と当接し、
スリンガーの第一の円環部は、芯金の円筒部の軸受内部側の遊端よりも軸受内部方向に位置するとともに、スリンガーの第一の円環部の遊端の内径寸法は、芯金の円筒部の遊端の外径寸法よりも小径となるように設定されていることを特徴とするパックシール。 An annular portion is integrally extended in the outer diameter direction from one end on the outer side of the cylindrical portion that is directly fitted to the outer diameter surface of the inner ring of the rolling bearing, and is configured in an L shape in cross section, and the elastic body is integrally formed. A vulcanized core with one or more lips;
Opposite to the cylindrical portion of the core metal, a cylindrical portion that fits with the inner diameter surface of the outer ring of the rolling bearing, and the one end of the cylindrical portion on the bearing inner side is integrally extended in the inner diameter direction. In a pack seal consisting of a slinger composed of a ring portion and a first ring portion facing the ring portion, the lip slides on the slinger.
The second annular part is integrally extended in the outer diameter direction from the other end of the cylindrical part of the slinger on the outer side of the bearing , and the second annular part is in contact with the end surface of the outer ring,
The first annular portion of the slinger is positioned in the bearing inner direction with respect to the free end of the cylindrical portion of the core metal inside the bearing, and the inner diameter dimension of the free end of the first ring portion of the slinger is the core metal A pack seal characterized by being set to have a smaller diameter than the outer diameter of the free end of the cylindrical portion . 芯金の円筒部は、転がり軸受の内輪の外径面と嵌合する第一の円筒部と、該第一の円筒部から、段差を有して前記第一の円筒部よりも大径に延設された第二の円筒部からなり、
スリンガーの第一の円環部の遊端は、芯金の円筒部の遊端側よりも軸受内部方向に位置し、芯金の第二の円筒部の遊端の外径寸法は、スリンガーの第一の円環部の遊端の内径寸法よりも大径となるように設定されていることを特徴とする請求項１に記載のパックシール。 The cylindrical portion of the core metal has a first cylindrical portion that fits to the outer diameter surface of the inner ring of the rolling bearing, and a larger diameter than the first cylindrical portion with a step from the first cylindrical portion. It consists of an extended second cylindrical part,
The free end of the first ring portion of the slinger is located closer to the bearing inside than the free end side of the cylindrical portion of the core metal, and the outer diameter of the free end of the second cylindrical portion of the core metal is The pack seal according to claim 1, wherein the pack seal is set to have a larger diameter than an inner diameter dimension of a free end of the first annular portion . 第二の円筒部の遊端の内径側には弾性体が一体に配され、内輪外径面との間にシールを構成していることを特徴とする請求項２に記載のパックシール。   The pack seal according to claim 2, wherein an elastic body is integrally disposed on the inner diameter side of the free end of the second cylindrical portion, and a seal is formed between the inner ring and the outer diameter surface of the inner ring. 請求項１〜請求項３のいずれかに記載のパックシールが適用された転がり軸受。
A rolling bearing to which the pack seal according to any one of claims 1 to 3 is applied.
JP2007118026A 2007-04-27 2007-04-27 Pack seal rolling bearing Expired - Fee Related JP4983374B2 (en)

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JP5233805B2 (en) * 2009-04-08 2013-07-10 株式会社ジェイテクト SEALING DEVICE AND ROLLING BEARING DEVICE USING THE SAME
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JPS5935729U (en) * 1982-08-31 1984-03-06 日本精工株式会社 Rolling bearing sealing device
JP2529956Y2 (en) * 1990-09-17 1997-03-26 日産ディーゼル工業株式会社 Structure of oil seal on axle of vehicle
JPH0599235A (en) * 1991-05-02 1993-04-20 Timken Co:The Seal assembly for antifriction bearing
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JP2001141069A (en) * 1999-11-17 2001-05-25 Ntn Corp Sealing device for rolling bearing
JP2003262233A (en) * 2002-03-08 2003-09-19 Yamada Seisakusho Co Ltd Sealing device of water pump bearing
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