JP2013050185A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP2013050185A
JP2013050185A JP2011188901A JP2011188901A JP2013050185A JP 2013050185 A JP2013050185 A JP 2013050185A JP 2011188901 A JP2011188901 A JP 2011188901A JP 2011188901 A JP2011188901 A JP 2011188901A JP 2013050185 A JP2013050185 A JP 2013050185A
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seal
rolling bearing
seal member
diameter
groove
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JP5800641B2 (en
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Shoichi Kinoshita
正一 木下
Hiroshi Komiyama
宏 小宮山
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Minebea 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
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • F16C33/7856—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race with a single sealing lip
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To improve assemblability while maintaining the retentivity and positionability of a seal in a sealing type rolling bearing having the seal.SOLUTION: In a rolling bearing 1, a plurality of balls 2 are fitted between the raceway groove 7 of an inner race 3 and the raceway groove 8 of an outer race 4. A seal member 5 is an annular member consisting of a composite body in which a core 12 is inserted in an elastic member 11, an outer circumferential part is fitted to and held by the seal groove 9 of the outer race 4, and a lip part 11b formed in an inner circumferential part is slidably brought into contact with or made to approach the outer circumferential surface of the inner race 3 to seal the inside of the bearing. The ratio (ride-over ratio α) of the difference (the ride-over amount C) between the outside diameter of the seal member 5 and the inside diameter of a seal inlet 9c lies in a range of 60-65% with respect to a difference K between the outside diameter of the core and the inside diameter of the seal inlet. Thus, the assemblability can be improved while maintaining the retentivity and the positionability of the seal member 5, and occurrence of any defective assembly when assembling the seal member by an automatic assembling machine can be prevented.

Description

本発明は、シール部材が装着された密封型の転がり軸受に関する。   The present invention relates to a sealed type rolling bearing equipped with a seal member.

転がり軸受には、異物の侵入、潤滑剤の漏れ等を防止するため、内輪と外輪の間にシール部材を装着して、内部を密封した密封型のものがある。密封型の転がり軸受として、例えば、特許文献１及び特許文献２に記載されているように、外輪に形成されたシール溝（内周溝）に、芯金がインサートされたゴム製のシール部材を嵌合、装着したものが公知である。このような芯金付のゴム製のシール部材は、自動組付機によって軸受本体に取付けることができるが、この場合、嵌合部のめくれ等の組付不良が発生する虞がある。   Some rolling bearings have a sealed type in which a sealing member is mounted between an inner ring and an outer ring to prevent foreign substances from entering and a lubricant from leaking. As a sealed rolling bearing, for example, as described in Patent Document 1 and Patent Document 2, a rubber seal member in which a metal core is inserted into a seal groove (inner circumferential groove) formed in an outer ring is used. What is fitted and mounted is known. Such a rubber seal member with a mandrel can be attached to the bearing main body by an automatic assembling machine, but in this case, there is a risk that assembly failure such as turning over of the fitting portion may occur.

そこで、例えば、特許文献１に記載されたものでは、シール溝の両端部の内径差と芯金の板厚との関係を最適化することにより、シール部材のシール溝への組付性及び位置決め性を改善している。また、特許文献２に記載されたものでは、シール部材の底面を傾斜させ、シール部材の傾斜面側を水平面に載置した際、周方向で線接触させることにより、シール部材の組付性及び径方向の位置決め精度を改善している。   Therefore, for example, in the one described in Patent Document 1, the assemblability and positioning of the seal member to the seal groove are optimized by optimizing the relationship between the inner diameter difference between both ends of the seal groove and the thickness of the core metal. Improves sex. Moreover, in what was described in patent document 2, when the bottom surface of the seal member is inclined and the inclined surface side of the seal member is placed on a horizontal surface, the seal member can be assembled by making line contact in the circumferential direction. The radial positioning accuracy has been improved.

特開２００４−１１６６８７号公報JP 2004-116687 A 特開平０９−６０６４６号公報JP 09-60646 A

このように、上述のような密封型の転がり軸受においては、シール部材の保持性及び位置決め性を維持しつつ、組付性を高め、組付不良の発生を防止することが望まれている。   As described above, in the above-described sealed type rolling bearing, it is desired to improve the assembling property and prevent the occurrence of an assembling failure while maintaining the retaining property and positioning property of the seal member.

本発明は、上記の点に鑑みてなされたものであり、シール部材の保持性及び位置決め性を維持しつつ、組付性を高めるようにした転がり軸受を提供することを目的とする。   The present invention has been made in view of the above points, and an object of the present invention is to provide a rolling bearing that is improved in assembling property while maintaining the retaining property and positioning property of the seal member.

上記の課題を解決するために、本発明は、内輪と外輪との間に複数の転動体を配置し、少なくとも一端側に前記内輪と前記外輪との間をシールするシール部材が設けられた密封型の転がり軸受において、
前記シール部材は、環状の芯金を弾性部材で被覆した構造で、前記外輪の内周面に形成されたシール溝に外周部が嵌合されて、内周部が前記内輪の外周面に摺接、又は、近接するように取付けられ、
前記外輪の前記シール溝の外側のシール入口の内径と前記芯金の外径との差に対して、前記シール部材の外径と前記シール入口との差の割合が６０％から６５％の範囲であることを特徴とする。 In order to solve the above-described problems, the present invention provides a sealing device in which a plurality of rolling elements are disposed between an inner ring and an outer ring, and a seal member is provided on at least one end side to seal between the inner ring and the outer ring. In rolling bearings of molds,
The seal member has a structure in which an annular metal core is covered with an elastic member, and an outer peripheral portion is fitted into a seal groove formed on an inner peripheral surface of the outer ring, and the inner peripheral portion slides on the outer peripheral surface of the inner ring. It is attached so that it is close or close,
The ratio of the difference between the outer diameter of the seal member and the seal inlet is 60% to 65% with respect to the difference between the inner diameter of the seal inlet outside the seal groove of the outer ring and the outer diameter of the cored bar. It is characterized by being.

本発明の転がり軸受によれば、シール部材の保持性及び位置決め性を維持しつつ、組付性を改善することができ、自動組付機で組付ける場合の組付不良を減少することができる。   According to the rolling bearing of the present invention, it is possible to improve the assembling property while maintaining the retaining property and the positioning property of the seal member, and to reduce the assembling defects when assembling with the automatic assembling machine. .

本発明の第１実施形態に係る転がり軸受の一端部の断面図である。It is sectional drawing of the one end part of the rolling bearing which concerns on 1st Embodiment of this invention. 本発明の第２実施形態に係る転がり軸受の一端部の断面図である。It is sectional drawing of the one end part of the rolling bearing which concerns on 2nd Embodiment of this invention. 鋼板製のシールドが組み付けられた図１に示す転がり軸受の一端部の断面図である。It is sectional drawing of the one end part of the rolling bearing shown in FIG. 1 with which the shield made from a steel plate was assembled | attached.

以下、本発明の実施形態を図面に基づいて詳細に説明する。
本発明の第１実施形態に係る転がり軸受の一端部の断面図を図１に示す。図１に示すように、転がり軸受１は、転動体であるボール（鋼球）２、内輪３、外輪４、シール部材５及び保持器６を備えている。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
A sectional view of one end of the rolling bearing according to the first embodiment of the present invention is shown in FIG. As shown in FIG. 1, the rolling bearing 1 includes a ball (steel ball) 2 that is a rolling element, an inner ring 3, an outer ring 4, a seal member 5, and a cage 6.

内輪３は、外周面に軌道溝７が形成され、一端側外周縁部に面取部３ａが形成されている。外輪４は、内周面に、内輪３の軌道溝７に対向して軌道溝８が形成され、また、一端側にシール部材５の外周部が嵌合されるシール溝９（内周溝）が形成されている。   The inner ring 3 has a raceway groove 7 formed on the outer peripheral surface, and a chamfered portion 3a formed on the outer peripheral edge portion on one end side. The outer ring 4 has a race groove 8 formed on the inner peripheral surface thereof so as to face the race groove 7 of the inner ring 3, and a seal groove 9 (inner circumference groove) in which the outer peripheral portion of the seal member 5 is fitted on one end side. Is formed.

内輪３の軌道溝７と外輪４の軌道溝８との間に複数のボール２が装填されて、保持器６によって所定の間隔で保持されている。   A plurality of balls 2 are loaded between the raceway groove 7 of the inner ring 3 and the raceway groove 8 of the outer ring 4 and held by the cage 6 at a predetermined interval.

シール溝９は、内側の小径溝９ａ及び外側の大径溝９ｂからなり、段部１０を有する段付形状で、大径溝９ｂの外側は、小径溝９ａと同径、又は、小径溝９ａよりもやや大径のシール入口９ｃとなっている。   The seal groove 9 includes an inner small-diameter groove 9a and an outer large-diameter groove 9b, and has a stepped shape having a step portion 10. The outer diameter of the large-diameter groove 9b is the same as or smaller than the small-diameter groove 9a. The seal inlet 9c has a slightly larger diameter.

シール部材５は、弾性部材１１に芯金１２をインサートした複合体からなる環状の部材である。シール部材５は、外周部がシール溝９に嵌合されて保持され、内周部に形成されたリップ部１１ｂを内輪３の外周面に摺接させて、軸受内部をシールする。シール部材５の転がり軸受１への装着前の形状を図中に破線で示す。なお、ここでは、転がり軸受１の一端側に設けられたシール部材５を図示しているが、シール部材５は、転がり軸受１の両端部に設けてもよい。シール部材５の外側面の外周部と中間部には、識別マークとして断面形状が略台形の溝１３が形成されている。この識別マークは、類似サイズの他機種用シール部材との見分けが容易にできるようにするためのものである。更に、弾性部材１１は、外周側にシール溝９に嵌合する嵌合部１１ａが形成され、内周側に内輪３に摺接するリップ部１１ｂが形成されている。   The seal member 5 is an annular member made of a composite body in which a core metal 12 is inserted into an elastic member 11. The seal member 5 is fitted and held in the outer periphery of the seal groove 9, and the lip portion 11 b formed in the inner periphery is brought into sliding contact with the outer periphery of the inner ring 3 to seal the inside of the bearing. The shape of the seal member 5 before being attached to the rolling bearing 1 is indicated by a broken line in the figure. Here, the sealing member 5 provided on one end side of the rolling bearing 1 is illustrated, but the sealing member 5 may be provided on both ends of the rolling bearing 1. A groove 13 having a substantially trapezoidal cross section is formed as an identification mark on the outer peripheral portion and the intermediate portion of the outer surface of the seal member 5. This identification mark is for making it easy to distinguish the seal member for other models of similar size. Furthermore, the elastic member 11 is formed with a fitting portion 11 a that fits in the seal groove 9 on the outer peripheral side, and a lip portion 11 b that is in sliding contact with the inner ring 3 on the inner peripheral side.

シール部材５の嵌合部１１ａの内側面の外周縁部には、段部１０に当接する傾斜面１５が形成されている。嵌合部１１ａは、シール溝９に挿入される芯金１２を覆うように形成されており、芯金１２の内側面の内周側は、弾性部材１１に覆われずに露出している。リップ部１１ｂは、弾性部材１１の外側面の内周部に形成されたＶ字溝１４と、内側面の内周縁部に形成された傾斜面１６によって薄肉のリップ状に形成されている。弾性部材１１の材質としては、例えば、ニトリルゴム等を使用することができる。   An inclined surface 15 that abuts on the stepped portion 10 is formed on the outer peripheral edge of the inner surface of the fitting portion 11 a of the seal member 5. The fitting portion 11 a is formed so as to cover the core metal 12 inserted into the seal groove 9, and the inner peripheral side of the inner surface of the core metal 12 is exposed without being covered by the elastic member 11. The lip portion 11b is formed into a thin lip shape by a V-shaped groove 14 formed on the inner peripheral portion of the outer surface of the elastic member 11 and an inclined surface 16 formed on the inner peripheral edge portion of the inner surface. As a material of the elastic member 11, for example, nitrile rubber or the like can be used.

芯金１２は、剛性を有する平板状の環状部材であり、弾性部材１１にインサートされて、シール部材５の形状を保持している。芯金１２の材質としては、例えば、冷間圧延鋼材（ＳＰＣＣ）や電気亜鉛めっき鋼板（ＳＥＣＣ）等を使用することができる。なお、芯金１２は、ボール２の直径が２ｍｍ以下の小径ベアリングには、スペース的に平板状であることが望ましいが、完全な平板状でなく、折曲部を有する形状でもよい。   The core metal 12 is a flat plate-like annular member having rigidity, and is inserted into the elastic member 11 to hold the shape of the seal member 5. As a material of the core metal 12, for example, a cold rolled steel (SPCC), an electrogalvanized steel sheet (SECC), or the like can be used. In addition, although it is desirable that the metal core 12 has a flat plate shape in terms of space for a small-diameter bearing in which the diameter of the ball 2 is 2 mm or less, the metal plate 12 may have a bent portion instead of a complete flat plate shape.

シール部材５が、転がり軸受１に装着されることにより、内輪３と外輪４とボール２とシール部材５との間に密封された空間が形成され、この空間内に各部を潤滑するためのグリース（潤滑剤）が封入されている。   When the seal member 5 is mounted on the rolling bearing 1, a sealed space is formed between the inner ring 3, the outer ring 4, the ball 2, and the seal member 5, and grease for lubricating each part in this space (Lubricant) is enclosed.

なお、上述のシール溝９の段部１０は、図３に示すように、外輪４にシール部材５の代わりに鋼板製のシールド１７を取付けるためのものである。この場合、鋼板製のシールド１７は、小径溝９ａに装着され、大径溝９ｂにスナップリング１８が装着されて固定される。これにより、本転がり軸受１は、シール部材５及び鋼板製のシールド１７の装着に兼用することができるように工夫されている。   In addition, the step part 10 of the above-mentioned seal groove 9 is for attaching the shield 17 made of a steel plate to the outer ring 4 instead of the seal member 5 as shown in FIG. In this case, the shield 17 made of steel plate is mounted in the small diameter groove 9a, and the snap ring 18 is mounted and fixed in the large diameter groove 9b. Thereby, this rolling bearing 1 is devised so that it can be combined with mounting | wearing with the sealing member 5 and the shield 17 made from a steel plate.

次に、転がり軸受１の各部の寸法について説明する。本実施形態では、一例として、転がり軸受外径Ｄ＝１０ｍｍ、転がり軸受内径Ｅ＝６ｍｍ、ボール２の直径＝１．１９ｍｍ、内輪外径Ｆ＝６．９４８ｍｍ、外輪内径＝Ｇ８．７３０ｍｍ、シール部材外径Ｈ＝９．４４０ｍｍ、設計上、シール部材５がシール溝９と接触する領域の径方向長さであるオーバーラップ量Ｉ＝０．０５１ｍｍ、シール入口９ｃの軸方向長さＪ＝０．１３２ｍｍ、組付前のシール部材内径と内輪外径Ｆとの差Ｌ＝０．０３４ｍｍ、嵌合部１１ａの外周部の厚さＭ＝０．１８０ｍｍ、嵌合部傾斜角度Ｎ＝４５°、嵌合部１１ａの傾斜面１５のｒ（アール）面取り寸法Ｏ＝０．０５０ｍｍ、芯金外径Ｐ＝９．０１２ｍｍ、芯金板厚Ｔ＝０．１５０ｍｍとし、シール部材外径Ｈとシール入口９ｃの内径との差である乗越え量Ｃ＝０．０８３ｍｍ、芯金外径Ｐとシール入口９ｃの内径との差Ｋ＝０．１３２ｍｍに設定している。   Next, the dimension of each part of the rolling bearing 1 will be described. In this embodiment, as an example, a rolling bearing outer diameter D = 10 mm, a rolling bearing inner diameter E = 6 mm, a ball 2 diameter = 1.19 mm, an inner ring outer diameter F = 6.948 mm, an outer ring inner diameter = G 8.730 mm, a seal member Outer diameter H = 9.440 mm, by design, overlap amount I = 0.051 mm, which is the radial length of the region where seal member 5 contacts seal groove 9, and axial length J = 0.01 mm of seal inlet 9 c. 132 mm, difference L between inner diameter of sealing member and inner ring outer diameter F before assembly L = 0.034 mm, thickness M of outer periphery of fitting portion 11a = 0.180 mm, fitting portion inclination angle N = 45 °, fitting The r (round) chamfer dimension O = 0.050 mm of the inclined surface 15 of the joint portion 11a, the core metal outer diameter P = 9.012 mm, the core metal plate thickness T = 0.150 mm, the seal member outer diameter H and the seal inlet 9c. Override amount that is the difference from the inner diameter of = 0.083 mm, is set to the difference K = 0.132 mm and the inside diameter of the core metal outer diameter P and the seal inlet 9c.

ここで、本発明では、芯金外径Ｐとシール入口９ｃの内径との差Ｋに対する乗越え量Ｃの割合を乗越え量率α（α＝Ｃ／Ｋ×１００）として、乗越え量率αを６０〜６５％の範囲とする。本実施形態では、芯金外径Ｐとシール入口９ｃの内径との差Ｋ＝０．１３２ｍｍ、乗越え量Ｃ＝０．０８３ｍｍであり、乗越え量率α＝６２．９％となった。   Here, in the present invention, the ratio of the overriding amount C to the difference K between the outer diameter P of the cored bar and the inner diameter of the seal inlet 9c is defined as the overriding amount rate α (α = C / K × 100). The range is -65%. In the present embodiment, the difference between the outer diameter P of the cored bar and the inner diameter of the seal inlet 9c is K = 0.132 mm, the overpassing amount C = 0.083 mm, and the overpassing rate α = 62.9%.

これにより、シール部材５をシール溝９に装着したとき、シール部材５の保持性及び位置決め性を維持しつつ、組付性を向上させることができる。実際に自動組付機を用いて転がり軸受１にシール部材５を組付けた場合、乗越え量率α＝６２．９％とした本実施形態では、不良率は、略０．０％となった。従来の転がり軸受において、乗越え量率α＝８５．５％とした場合の不良率は、０．５３％であったが、本実施形態により、組付不良を大幅に低減することができた。   Thereby, when the seal member 5 is mounted in the seal groove 9, the assembling property can be improved while maintaining the retaining property and the positioning property of the seal member 5. When the seal member 5 is actually assembled to the rolling bearing 1 using an automatic assembling machine, the defect rate is substantially 0.0% in the present embodiment in which the overloading rate α is 62.9%. . In the conventional rolling bearing, the defective rate when the over-ride amount rate α = 85.5% was 0.53%, but according to this embodiment, it was possible to greatly reduce the defective assembly.

次に、本発明の第２実施形態について、図２を参照して説明する。なお、以下の説明において、上記第１実施形態に対して、同様の部分には同じ参照符号を用いて、異なる部分についてのみ詳細に説明する。   Next, a second embodiment of the present invention will be described with reference to FIG. In the following description, the same reference numerals are used for the same parts with respect to the first embodiment, and only different parts will be described in detail.

図２に示すように、本実施形態の転がり軸受１Ａでは、シール部材５は、弾性部材１１によって芯金１２が完全に被覆されている。シール部材５の嵌合部１１ａは、外周部が傾斜面１５になっており、リップ部１１ｂは、外側寄りに配置されて、略四角形の断面形状を有している。   As shown in FIG. 2, in the rolling bearing 1 </ b> A of the present embodiment, the seal member 5 is completely covered with the core metal 12 by the elastic member 11. As for the fitting part 11a of the seal member 5, the outer peripheral part becomes the inclined surface 15, and the lip part 11b is arrange | positioned near the outer side, and has a substantially square cross-sectional shape.

本実施形態の転がり軸受１Ａの各部の寸法は、乗越え量Ｃ＝０．１０２ｍｍ、転がり軸受外径Ｄ＝９ｍｍ、転がり軸受内径Ｅ＝４ｍｍ、ボール２の直径＝１．５９ｍｍ、外輪内径Ｇ＝７．４８０ｍｍ、オーバーラップ量Ｉ＝０．０７３ｍｍ、シール入口９ｃの軸方向長さＪ＝０．１９４ｍｍ、芯金外径とシール入口内径との差Ｋ＝０．１６５ｍｍとなっている。したがって、乗越え量率α（α＝Ｃ／Ｋ×１００）は、６１．８％である。これにより、上記第１実施形態と同様の作用効果を奏することができる。   The dimensions of each part of the rolling bearing 1A of the present embodiment are as follows: the amount of climbing C = 0.102 mm, the outer diameter D of the rolling bearing D = 9 mm, the inner diameter E of the rolling bearing E = 4 mm, the diameter of the ball 2 = 1.59 mm, and the inner diameter G of the outer ring G = 7. .480 mm, overlap amount I = 0.073 mm, axial length J = 0.194 mm of the seal inlet 9c, and the difference K = 0.165 mm between the outer diameter of the metal core and the inner diameter of the seal inlet. Therefore, the overpass rate α (α = C / K × 100) is 61.8%. Thereby, there can exist an effect similar to the said 1st Embodiment.

なお、本発明は、上述した第１及び第２実施形態に限定されるものではなく、適宜、変更、改良などが可能である。例えば、転動体がボール２である玉軸受を一例に説明したが、玉軸受に限定されるものではなく、ころ軸受など、他の転がり軸受にも適用することができる。また、シール部材５のリップ部１１ｂが内輪３の外周面に摺接（接触）するもので説明したが、近接（非接触）するものにも適用することができる。   The present invention is not limited to the first and second embodiments described above, and can be changed or improved as appropriate. For example, although the ball bearing in which the rolling element is the ball 2 has been described as an example, the present invention is not limited to the ball bearing, and can be applied to other rolling bearings such as a roller bearing. Moreover, although the lip portion 11b of the seal member 5 has been described as being in sliding contact (contact) with the outer peripheral surface of the inner ring 3, it can also be applied to the case in which the lip portion 11b is in proximity (non-contact).

１…転がり軸受、２…ボール（転動体）、３…内輪、４…外輪、５…弾性シール（シール部材）、９ｃ…シール入口、１１…弾性部材、１２…芯金、Ｃ…乗越え量、Ｋ…芯金外径とシール入口内径との差   DESCRIPTION OF SYMBOLS 1 ... Rolling bearing, 2 ... Ball (rolling element), 3 ... Inner ring, 4 ... Outer ring, 5 ... Elastic seal (seal member), 9c ... Seal inlet, 11 ... Elastic member, 12 ... Core metal, C ... Override amount, K: Difference between the outer diameter of the metal core and the inner diameter of the seal inlet

Claims (3)

内輪と外輪との間に複数の転動体を配置し、少なくとも一端側に前記内輪と前記外輪との間をシールするシール部材が設けられた密封型の転がり軸受において、
前記シール部材は、環状の芯金を弾性部材で被覆した構造で、前記外輪の内周面に形成されたシール溝に外周部が嵌合されて、内周部が前記内輪の外周面に摺接、又は、近接するように取付けられ、
前記外輪の前記シール溝の外側のシール入口の内径と前記芯金の外径との差に対して、前記シール部材の外径と前記シール入口との差の割合が６０％から６５％の範囲であることを特徴とする転がり軸受。 In a sealed type rolling bearing in which a plurality of rolling elements are disposed between an inner ring and an outer ring, and a seal member that seals between the inner ring and the outer ring is provided on at least one end side.
The seal member has a structure in which an annular metal core is covered with an elastic member, and an outer peripheral portion is fitted into a seal groove formed on an inner peripheral surface of the outer ring, and the inner peripheral portion slides on the outer peripheral surface of the inner ring. It is attached so that it is close or close,
The ratio of the difference between the outer diameter of the seal member and the seal inlet is 60% to 65% with respect to the difference between the inner diameter of the seal inlet outside the seal groove of the outer ring and the outer diameter of the cored bar. A rolling bearing characterized by being 前記環状の芯金は、平板状であることを特徴とする請求項１に記載の転がり軸受。   The rolling bearing according to claim 1, wherein the annular cored bar has a flat plate shape. 前記転動体は、直径２ｍｍ以下であることを特徴とする請求項１又は２に記載の転がり軸受。   The rolling bearing according to claim 1, wherein the rolling element has a diameter of 2 mm or less.
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015007465A (en) * 2013-06-26 2015-01-15 Ntn株式会社 Seal for bearing
KR101782219B1 (en) * 2015-10-19 2017-09-26 셰플러코리아(유) A rolling bearing
US20220142733A1 (en) * 2019-03-28 2022-05-12 Nsk Ltd. Roller bearing

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0651555U (en) * 1992-12-22 1994-07-15 日本精工株式会社 Ball bearing with seal
JPH07279978A (en) * 1994-04-06 1995-10-27 Uchiyama Mfg Corp Bearing seal

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0651555U (en) * 1992-12-22 1994-07-15 日本精工株式会社 Ball bearing with seal
JPH07279978A (en) * 1994-04-06 1995-10-27 Uchiyama Mfg Corp Bearing seal

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015007465A (en) * 2013-06-26 2015-01-15 Ntn株式会社 Seal for bearing
KR101782219B1 (en) * 2015-10-19 2017-09-26 셰플러코리아(유) A rolling bearing
US20220142733A1 (en) * 2019-03-28 2022-05-12 Nsk Ltd. Roller bearing
US11877899B2 (en) * 2019-03-28 2024-01-23 Nsk Ltd. Roller bearing

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