JP2013104507A - Sealing rolling bearing - Google Patents

Sealing rolling bearing Download PDF

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JP2013104507A
JP2013104507A JP2011249876A JP2011249876A JP2013104507A JP 2013104507 A JP2013104507 A JP 2013104507A JP 2011249876 A JP2011249876 A JP 2011249876A JP 2011249876 A JP2011249876 A JP 2011249876A JP 2013104507 A JP2013104507 A JP 2013104507A
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Prior art keywords
shield
outer ring
rolling bearing
fitting
peripheral surface
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JP5895462B2 (en
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Go Okunaga
剛 奥永
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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
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7813—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for tapered roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/783—Details of the sealing or parts thereof, e.g. geometry, material of the mounting region
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Of Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a sealing rolling bearing which can suppress the deformation of an outer peripheral surface of an outer ring caused by the attachment of a shield while preventing the shield from dropping, and can further suppress a variation of a deformation amount caused by a variation of fitting margins.SOLUTION: In a sealing rolling bearing, a fitting margin of an outer ring 1 and a shield 31 is set so that stress which is generated at fitting at a corner 31e located between a fixed part 31a and an extending part 31d extending by being bent toward an inner radial direction from the fixed part 31a is equal to or larger than yield stress.

Description

本発明は、密封型転がり軸受に関し、より詳細には、鉄道車両などの振動荷重環境下で使用される密封型転がり軸受に関する。   The present invention relates to a sealed rolling bearing, and more particularly to a sealed rolling bearing used in a vibration load environment such as a railway vehicle.

鉄道車両の車軸の端部には鉄道車両用転がり軸受ユニットが取り付けられており、車軸を回転自在に支持するとともに車両の重量を支えている。図７は、従来の鉄道車両用転がり軸受ユニットを示す。   A rolling bearing unit for a railway vehicle is attached to an end portion of the axle of the railway vehicle, and rotatably supports the axle and supports the weight of the vehicle. FIG. 7 shows a conventional rolling bearing unit for railway vehicles.

この鉄道車両用転がり軸受ユニットは、鉄道車両に用いられる転がり軸受の一例である複列円錐ころ軸受１０（以降、軸受１０と称す）を備えており、この軸受１０に鉄道車両の車軸２０が支持されている。軸受１０は、一体型の外輪１と各列に個別に分割された内輪２，２とを備え、内輪２と外輪１との間には、保持器４に保持された複数のころ（転動体）３が転動自在に配置されている。そして、軸受１０の軸方向両端側には、後蓋（又はバッキングリング）６及び前蓋７が内輪２，２の側面と当接するように配置されている。   This rolling bearing unit for a railway vehicle includes a double row tapered roller bearing 10 (hereinafter referred to as a bearing 10) which is an example of a rolling bearing used in a railway vehicle, and the axle 20 of the railway vehicle supports the bearing 10. Has been. The bearing 10 includes an integrated outer ring 1 and inner rings 2 and 2 that are individually divided into rows, and a plurality of rollers (rolling elements) held by a cage 4 are provided between the inner ring 2 and the outer ring 1. ) 3 is arranged to roll freely. A rear lid (or backing ring) 6 and a front lid 7 are disposed at both axial ends of the bearing 10 so as to contact the side surfaces of the inner rings 2 and 2.

後蓋６及び前蓋７の軸受寄りの外周側には、段付き円筒状のシールド３１が外輪１に嵌合されて配置されている。シールド３１の内周側には、環状のシール３２が取り付けられている。即ち、シール３２の外周側がシールド３１の内周面に固着され、シール３２の内周側が後蓋６または前蓋７の外周面に摺接している。これにより、軸受１０が密封され、内部にごみ、水分、異物等が外部から侵入することを防ぐとともに、軸受１０内のグリース等の潤滑剤が外部に漏出するのを防いでいる。   On the outer peripheral side of the rear lid 6 and the front lid 7 near the bearings, a stepped cylindrical shield 31 is fitted and disposed on the outer ring 1. An annular seal 32 is attached to the inner peripheral side of the shield 31. That is, the outer peripheral side of the seal 32 is fixed to the inner peripheral surface of the shield 31, and the inner peripheral side of the seal 32 is in sliding contact with the outer peripheral surface of the rear lid 6 or the front lid 7. As a result, the bearing 10 is sealed, and dust, moisture, foreign matter, and the like are prevented from entering from the outside, and a lubricant such as grease in the bearing 10 is prevented from leaking to the outside.

図８（ａ）〜（ｃ）は、特許文献１に記載のシールドが装着された種々の密封型転がり軸受を示す。図８（ａ）に示すシールド３１は、外輪１の肩部の内周面１ａに圧入固定された筒状の固定部３１ａと、固定部３１ａから外輪１の軸方向外側に延びるとともにシール３２が保持される筒状の保持部３１ｂとを有する。また、固定部３１ａの端部には、径方向に突出した突起部３１ｃが形成され、肩部に形成されたシール溝１ｂに係合し、シールド３１の軸方向への移動が規制されている。   8A to 8C show various sealed rolling bearings to which the shield described in Patent Document 1 is attached. The shield 31 shown in FIG. 8A includes a cylindrical fixing portion 31a that is press-fitted and fixed to the inner peripheral surface 1a of the shoulder portion of the outer ring 1, and extends outward from the fixing portion 31a in the axial direction of the outer ring 1 and a seal 32. And a cylindrical holding portion 31b to be held. Further, a protruding portion 31c projecting in the radial direction is formed at the end portion of the fixed portion 31a, and engages with the seal groove 1b formed in the shoulder portion, thereby restricting the movement of the shield 31 in the axial direction. .

また、図８（ｂ）及び図８（ｃ）に示すシールド３１は、固定部３１ａが先端に向かって拡径するテーパ面を有し、弾性的に縮径した状態で、外輪１の肩部の内周面１ａとシール溝１ｂとの間に形成される環状角部１ｃに内嵌され、環状角部１ｃと固定部３１ａの外周面とが線接触することで、外輪１に固定されている。また、固定部３１ａの先端には、径方向外側に突出して、シール溝１ｂに係合する突起部３１ｃが形成されている。   Further, the shield 31 shown in FIGS. 8B and 8C has a tapered surface where the fixed portion 31a expands toward the tip, and the shoulder portion of the outer ring 1 is elastically reduced in diameter. Is fixed to the outer ring 1 by linearly contacting the annular corner portion 1c and the outer peripheral surface of the fixing portion 31a. Yes. In addition, a protrusion 31c that protrudes radially outward and engages with the seal groove 1b is formed at the tip of the fixed portion 31a.

特開２００８−２４０７８１号公報JP 2008-240781 A

ところで、転がり軸受のシールドは、特に鉄道車両用といった振動環境下で使用される場合、シールドが振動によって脱落しないようはめあい代を大きく設定する必要がある。その結果、シールドの装着によって外輪が変形し易くなる為、外輪を一定の公差範囲に入れることが困難になると同時に、公差を確保した場合でも外輪とハウジング間での片当たりが発生する結果、外輪外周面にフレッティング損傷が発生する懸念があった。   By the way, when the shield of a rolling bearing is used in a vibration environment, particularly for a railway vehicle, it is necessary to set a large fitting allowance so that the shield does not fall off due to vibration. As a result, the outer ring is easily deformed by the installation of the shield, making it difficult to put the outer ring within a certain tolerance range. At the same time, even if the tolerance is secured, the outer ring and the housing will be in contact with each other. There was concern that fretting damage would occur on the outer peripheral surface.

このハウジングとの外輪はめあい部分への変形の影響を軽減する方法として、シールド装着部分に対応する外輪外周面に逃げを設ける方法が一般に採用されるが、その場合でもシールドと外輪間のはめあいによって発生する力が大きい場合、この逃げ以外の外輪外周面にも変形が波及し、その結果、ハウジングと接触する外輪外周面に部分的なかじりが発生する可能性があった。   As a method to reduce the influence of deformation on the outer ring fitting portion with the housing, a method of providing relief on the outer ring outer peripheral surface corresponding to the shield mounting portion is generally adopted, but even in this case, it occurs due to the fit between the shield and the outer ring. When the force to be applied is large, the deformation also affects the outer ring outer peripheral surface other than the relief, and as a result, the outer ring outer peripheral surface contacting the housing may partially galling.

また、図８（ａ）に示すシールド３１は、はめあいによって発生する力が大きい場合、外輪外周面の変形量を抑制することができないため、締め代をあまり大きくできないことから、シールド３１が脱落する可能性があった。さらに、図８（ｂ）及び図８（ｃ）に示すシールドは、固定部３１ａが線接触のため、シールド３１の姿勢が不安定であり、接触面に応力集中が発生しやすい。また、固定部３１ａの外周面は、テーパ面のため、外輪１に挿入し難い。   Further, in the shield 31 shown in FIG. 8A, when the force generated by fitting is large, the deformation amount of the outer peripheral surface of the outer ring cannot be suppressed, so that the tightening margin cannot be increased so that the shield 31 falls off. There was a possibility. Further, in the shield shown in FIGS. 8B and 8C, since the fixed portion 31a is in line contact, the posture of the shield 31 is unstable, and stress concentration tends to occur on the contact surface. Moreover, since the outer peripheral surface of the fixing | fixed part 31a is a taper surface, it is hard to insert in the outer ring | wheel 1.

本発明は、上記事情に鑑みてなされたものであり、その目的は、シールドの脱落防止を図るとともに、シールド装着によって発生する外輪外周面の変形を抑制することができ、はめあい代のばらつきによって生じる変形量のばらつきも抑えることができる密封型転がり軸受を提供することにある。   The present invention has been made in view of the above circumstances, and an object of the present invention is to prevent the shield from falling off and to suppress the deformation of the outer peripheral surface of the outer ring caused by the installation of the shield. It is an object of the present invention to provide a sealed type rolling bearing capable of suppressing variation in deformation amount.

本発明の上記目的は、下記の構成により達成される。
（１） 外輪、内輪、及び、前記外輪と前記内輪との間に転動自在に配置される複数の転動体と、前記外輪の外周面又は内周面としめしろ嵌合する固定部を有するシールドと、
を備えた密封型転がり軸受において、
前記外輪と前記シールドとのはめあい代は、前記固定部と、前記固定部から径方向内方に折り曲げられて延伸する延伸部との間の隅部におけるはめあい時の応力が降伏応力以上となるように設定されていることを特徴とする密封型転がり軸受。 The above object of the present invention can be achieved by the following constitution.
(1) It has an outer ring, an inner ring, and a plurality of rolling elements that are arranged so as to be able to roll between the outer ring and the inner ring, and a fixing portion that fits to the outer peripheral surface or inner peripheral surface of the outer ring. A shield,
In a sealed type rolling bearing with
The fitting allowance between the outer ring and the shield is such that the stress at the time of fitting at the corner between the fixed portion and the extending portion that is bent radially inward from the fixed portion is equal to or greater than the yield stress. Sealed type rolling bearing characterized by being set to.

本発明の密封型転がり軸受によれば、外輪とシールドとのはめあい代は、隅部におけるはめあい時の応力が降伏応力以上となるように設定されているので、隅部の応力の許容範囲内ではめあい代を大きく設定して、シールドの脱落防止を図るとともに、シールド装着によって発生する外輪外周面の変形を抑制することができる。また、はめあい代のばらつきによる発生応力の変動も弾性変形の場合より小さくなる為、外輪の局部的変形（そり）のばらつきも小さくすることができる。   According to the sealed type rolling bearing of the present invention, the fitting allowance between the outer ring and the shield is set so that the stress at the fitting at the corner is equal to or greater than the yield stress, so that the stress within the corner is within the allowable range. A large fitting allowance can be set to prevent the shield from falling off, and deformation of the outer peripheral surface of the outer ring caused by mounting the shield can be suppressed. Further, since the fluctuation of the generated stress due to the variation in the fitting allowance is smaller than that in the case of elastic deformation, the variation in the local deformation (warping) of the outer ring can be reduced.

本発明の密封型転がり軸受としての円錐ころ軸受を示す要部拡大断面図である。It is a principal part expanded sectional view which shows the tapered roller bearing as a sealing type rolling bearing of this invention. 本発明のしめしろと外輪変形量の関係を模式的に示すグラフである。It is a graph which shows typically the relation between the interference of the present invention and the amount of deformation of an outer ring. 本発明の密封型転がり軸受としての深溝玉軸受を示す要部拡大断面図である。It is a principal part expanded sectional view which shows the deep groove ball bearing as a sealing type rolling bearing of this invention. （ａ）及び（ｂ）は、本発明の密封型転がり軸受としての円筒ころ軸受を示す要部拡大断面図である。(A) And (b) is a principal part expanded sectional view which shows the cylindrical roller bearing as a sealing type rolling bearing of this invention. （ａ）は、試験に使用された密封型転がり軸受を示す要部拡大断面図であり、であり、（ｂ）は、しめしろと外輪変形量の関係を示すグラフである。(A) is a principal part expanded sectional view which shows the sealing type rolling bearing used for the test, (b) is a graph which shows the relationship between interference and an outer ring deformation amount. （ａ）〜（ｃ）は、本発明の密封型転がり軸受としての円錐ころ軸受、深溝玉軸受、円筒ころ軸受をそれぞれ示す要部拡大断面図である。(A)-(c) is a principal part expanded sectional view which respectively shows the tapered roller bearing, deep groove ball bearing, and cylindrical roller bearing as a sealing type rolling bearing of this invention. 従来の鉄道車両用転がり軸受ユニットの断面図である。It is sectional drawing of the conventional rolling bearing unit for rail vehicles. （ａ）〜（ｃ）は、従来の密封型転がり軸受を示す要部断面図である。(A)-(c) is principal part sectional drawing which shows the conventional sealed type rolling bearing.

以下、本発明に係る密封型転がり軸受の一実施形態について図面に基づいて詳細に説明する。なお、本発明の密封型転がり軸受は、従来技術として説明した図７に記載の鉄道車両用軸受ユニットにも適用可能であり、従来技術と実質的に同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。   Hereinafter, an embodiment of a sealed type rolling bearing according to the present invention will be described in detail with reference to the drawings. The sealed rolling bearing of the present invention can also be applied to the railway vehicle bearing unit shown in FIG. 7 described as the prior art, and parts substantially the same as or equivalent to the prior art are denoted by the same reference numerals in the drawings. The description is omitted or simplified.

本実施形態の円錐ころ軸受（密封型転がり軸受）１０では、図１に示すように、外輪１の肩部の外周面に、小径部１ｄが形成されており、この小径部１ｄの外周面１ｅにシールド３１の固定部３１ａの内周面が嵌合している。小径部１ｄの外径は、シールド３１が装着された外輪１が図示しないハウジングに内嵌された際に、シールド３１の外周面がハウジングと干渉しないように設定されている。   In the tapered roller bearing (sealed rolling bearing) 10 of the present embodiment, as shown in FIG. 1, a small diameter portion 1d is formed on the outer peripheral surface of the shoulder portion of the outer ring 1, and the outer peripheral surface 1e of the small diameter portion 1d. The inner peripheral surface of the fixing portion 31a of the shield 31 is fitted in The outer diameter of the small diameter portion 1d is set so that the outer peripheral surface of the shield 31 does not interfere with the housing when the outer ring 1 to which the shield 31 is attached is fitted in a housing (not shown).

また、シールド３１は、外輪１の軸方向端面と当接するように、固定部３１ａから径方向内方に折り曲げられて延伸する延伸部３１ｄを有している。ここで、外輪１の小径部１ｄとシールド３１の固定部３１ａとは、円筒部３１ａと延伸部３１ｄとの間の湾曲した隅部３１ｅ（以下、隅Ｒ部３１ｅと称す。）におけるはめあい時の応力が降伏応力以上になるように、はめあい代が設定されている。   Further, the shield 31 has an extending portion 31 d that is bent and extended radially inward from the fixed portion 31 a so as to contact the axial end surface of the outer ring 1. Here, the small diameter portion 1d of the outer ring 1 and the fixing portion 31a of the shield 31 are fitted at a curved corner portion 31e (hereinafter referred to as a corner R portion 31e) between the cylindrical portion 31a and the extending portion 31d. The fitting allowance is set so that the stress is equal to or greater than the yield stress.

このように、シールド３１が挿入される外輪１とのはめあい面のはめあい代を、応力が集中する隅Ｒ部３１ｅで降伏応力以上となるように設定した場合、はめあい代とはめあい部の応力の関係が弾塑性となる為、はめあい代増大に対する発生応力の増大分が弾性変形の場合より小さくなる。その結果、隅Ｒ部３１ｅの応力の許容範囲内ではめあい代を大きく設定できることができ、また、はめあい代のばらつきによる発生応力の変動も弾性変形の場合より小さくなる為、外輪１の局部的変形（そり）のばらつきも小さくすることができる。
なお、はめあい代の上限は、シールドの強度及び鉄道車両用軸受の設計しめしろ範囲を考慮して、しめしろ／嵌合部外径（小径部１ｄの外径、固定部３１ａの内径）の比で、０．００３に設定される。 In this way, when the fitting allowance of the fitting surface with the outer ring 1 into which the shield 31 is inserted is set to be equal to or greater than the yield stress at the corner R portion 31e where the stress is concentrated, the relationship between the fitting allowance and the stress of the fitting portion. Is elasto-plastic, so the increase in the generated stress with respect to the increase in the fitting allowance is smaller than in the case of elastic deformation. As a result, the fitting allowance can be set large within the allowable range of the stress at the corner R portion 31e, and the fluctuation of the generated stress due to the variation in the fitting allowance is smaller than that in the case of elastic deformation. Variation in (sledge) can also be reduced.
The upper limit of the fitting allowance is a ratio of the interference / fitting portion outer diameter (the outer diameter of the small diameter portion 1d and the inner diameter of the fixing portion 31a) in consideration of the strength of the shield and the design interference range of the bearing for the railway vehicle. Therefore, it is set to 0.003.

図２は、上述した本発明の効果を模式的に示す。しめしろｄ１からｄ２において、はめあい代とはめあい部の応力の関係が弾性の場合には外輪変形量はＡになるが、はめあい代とはめあい部の応力の関係が弾塑性の場合には、ｄ１以上で隅Ｒ部３１ｅの応力が降伏応力以上となるため、外輪変形量はＢとなり弾性の場合に比べて外輪変形量を大幅に抑制できる。   FIG. 2 schematically shows the effects of the present invention described above. In the interference d1 to d2, the outer ring deformation amount is A when the relationship between the fitting margin and the stress at the fitting portion is elastic, but when the relationship between the fitting margin and the stress at the fitting portion is elastoplastic, it is d1 or more. Since the stress at the corner R portion 31e is equal to or greater than the yield stress, the outer ring deformation amount is B, and the outer ring deformation amount can be significantly suppressed as compared with the case of elasticity.

なお、密封型転がり軸受としては、図１の円錐ころ軸受１０に限らず、図３に示す深溝玉軸受１０Ａや、図４に示す円筒ころ軸受１０Ｂであっても、シールド３１の隅Ｒ部３１ｅにおけるはめあい応力が降伏応力以上になるようにはめあい代を設定することで同様の効果が得られる。なお、シールド３１は、図４（ａ）に示すように、延伸部３１ｄが段付き形状によって２箇所に設けられてもよく、図４（ｂ）に示すように、延伸部３１ｄが１箇所に設けられるものであっても良い。   The sealed rolling bearing is not limited to the tapered roller bearing 10 shown in FIG. 1, but may be a deep groove ball bearing 10A shown in FIG. 3 or a cylindrical roller bearing 10B shown in FIG. The same effect can be obtained by setting the fitting allowance so that the fitting stress in Y is greater than the yield stress. In addition, as shown in FIG. 4A, the shield 31 may be provided with two extending portions 31d in a stepped shape, and as shown in FIG. 4B, the extending portion 31d is provided in one location. It may be provided.

図５は、図４（ｂ）の円筒ころ軸受に本発明を適用した場合の解析値と実測値を示す。軸受緒元は図５（ａ）に示す通りで、外輪変形量は軸端から１４．５ｍｍの値を採用している。図５（ｂ）に示す結果から、隅Ｒ部３１ｅの応力が降伏応力以上となる領域(しめしろ０．１ｍｍ以上)で、外輪の変形量(実測値)は大きく抑制されていることがわかる。
なお、鉄道車両用で使用されるシールド３１としては、ＳＰＣＣのような鋼材が使用されているが、図５の解析及び実験では、ＳＵＳ３０４を使用している。 FIG. 5 shows analysis values and actual measurement values when the present invention is applied to the cylindrical roller bearing of FIG. The bearing specifications are as shown in FIG. 5A, and the outer ring deformation amount is 14.5 mm from the shaft end. From the result shown in FIG. 5B, it is understood that the deformation amount (actually measured value) of the outer ring is greatly suppressed in a region where the stress at the corner R portion 31e is equal to or higher than the yield stress (interference of 0.1 mm or more). .
Note that a steel material such as SPCC is used as the shield 31 used for the railway vehicle, but SUS304 is used in the analysis and experiment of FIG.

なお、本発明は、前述した各実施形態に限定されるものでなく、適宜、変形、改良等が可能である。   In addition, this invention is not limited to each embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

上記実施形態では、外輪１の外周面にシールド３１を嵌合する場合を示したが、図６（ａ）〜（ｃ）に示すように、円筒ころ軸受、深溝玉軸受、円すいころ軸受の外輪１の肩部の内周面１ａに、シールド３１の隅Ｒ部３１ｅにおけるはめあい時の応力が降伏応力以上になるようにはめあいを設定することによって、同様の効果が得られる。
また、図６（ａ）に示すように、固定部３１ａの先端には、径方向外側に突出して、シール溝１ｂに係合する突起部３１ｃが形成されてもよい。 In the above embodiment, the case where the shield 31 is fitted to the outer peripheral surface of the outer ring 1 is shown. However, as shown in FIGS. 6A to 6C, the outer ring of the cylindrical roller bearing, the deep groove ball bearing, and the tapered roller bearing. The same effect can be obtained by setting the fitting so that the stress at the time of fitting at the corner R portion 31e of the shield 31 is equal to or higher than the yield stress on the inner peripheral surface 1a of the shoulder 1 of the first shoulder.
Moreover, as shown to Fig.6 (a), the protrusion part 31c which protrudes to radial direction outer side and engages with the seal groove 1b may be formed in the front-end | tip of the fixing | fixed part 31a.

また、図７に示すシールド３１は、シール３２が取り付けられることで、軸受１０を密封しているが、シールド３１によって軸受１０を密封する構成であってもよい。   Moreover, although the shield 31 shown in FIG. 7 seals the bearing 10 by attaching the seal 32, the bearing 10 may be sealed by the shield 31.

１ 外輪
１ａ 内周面
１ｅ 外周面
２ 内輪
３ ころ（転動体）
１０ 複列円錐ころ軸受（密封型転がり軸受）
１０Ａ 深溝玉軸受
１０Ｂ 円筒ころ軸受
３１ シールド
３１ａ 固定部
３１ｄ 延伸部
３１ｅ 隅Ｒ部（隅部） DESCRIPTION OF SYMBOLS 1 Outer ring 1a Inner peripheral surface 1e Outer peripheral surface 2 Inner ring 3 Roller (rolling element)
10 Double row tapered roller bearing (sealed type rolling bearing)
10A Deep groove ball bearing 10B Cylindrical roller bearing 31 Shield 31a Fixing part 31d Extension part 31e Corner R part (corner part)

Claims (1)

外輪、内輪、及び、前記外輪と前記内輪との間に転動自在に配置される複数の転動体と、前記外輪の外周面又は内周面としめしろ嵌合する固定部を有するシールドと、
を備えた密封型転がり軸受において、
前記外輪と前記シールドとのはめあい代は、前記固定部と、前記固定部から径方向内方に折り曲げられて延伸する延伸部との間の隅部におけるはめあい時の応力が降伏応力以上となるように設定されていることを特徴とする密封型転がり軸受。 An outer ring, an inner ring, and a plurality of rolling elements that are arranged to freely roll between the outer ring and the inner ring, and a shield having a fixing portion that fits together with an outer peripheral surface or an inner peripheral surface of the outer ring;
In a sealed type rolling bearing with
The fitting allowance between the outer ring and the shield is such that the stress at the time of fitting at the corner between the fixed portion and the extending portion that is bent radially inward from the fixed portion is equal to or greater than the yield stress. Sealed type rolling bearing characterized by being set to.
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104343826A (en) * 2013-08-02 2015-02-11 Skf公司 Sealing device for a hub-wheel assembly
CN104865733A (en) * 2015-06-01 2015-08-26 青岛海信电器股份有限公司 Gasket used for shading module corner, module and display device
JP5812202B1 (en) * 2014-05-30 2015-11-11 日本精工株式会社 Ball screw device
JP2016094982A (en) * 2014-11-13 2016-05-26 株式会社ジェイテクト Revolving seat bearing

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Publication number Priority date Publication date Assignee Title
JPS6323070A (en) * 1986-06-19 1988-01-30 Arai Pump Mfg Co Ltd Oil seal of outer peripheral metal fitting type
JP2003269471A (en) * 2002-03-18 2003-09-25 Nsk Ltd Bearing device for railway vehicle
JP2006064145A (en) * 2004-08-30 2006-03-09 Ntn Corp Bearing device for wheel
JP2008309278A (en) * 2007-06-15 2008-12-25 Nsk Ltd Bearing unit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6323070A (en) * 1986-06-19 1988-01-30 Arai Pump Mfg Co Ltd Oil seal of outer peripheral metal fitting type
JP2003269471A (en) * 2002-03-18 2003-09-25 Nsk Ltd Bearing device for railway vehicle
JP2006064145A (en) * 2004-08-30 2006-03-09 Ntn Corp Bearing device for wheel
JP2008309278A (en) * 2007-06-15 2008-12-25 Nsk Ltd Bearing unit

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104343826A (en) * 2013-08-02 2015-02-11 Skf公司 Sealing device for a hub-wheel assembly
CN104343826B (en) * 2013-08-02 2017-12-15 Skf公司 The sealing device of hub unit
JP5812202B1 (en) * 2014-05-30 2015-11-11 日本精工株式会社 Ball screw device
WO2015181860A1 (en) * 2014-05-30 2015-12-03 日本精工株式会社 Ball-screw device
JP2016094982A (en) * 2014-11-13 2016-05-26 株式会社ジェイテクト Revolving seat bearing
CN104865733A (en) * 2015-06-01 2015-08-26 青岛海信电器股份有限公司 Gasket used for shading module corner, module and display device

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