JP2010002017A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
JP2010002017A
JP2010002017A JP2008162703A JP2008162703A JP2010002017A JP 2010002017 A JP2010002017 A JP 2010002017A JP 2008162703 A JP2008162703 A JP 2008162703A JP 2008162703 A JP2008162703 A JP 2008162703A JP 2010002017 A JP2010002017 A JP 2010002017A
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Prior art keywords
seal
inclined surface
lip portion
rolling bearing
housing groove
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JP2008162703A
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JP2010002017A5 (en
Inventor
Yasuhiro Sakamoto
康裕 阪本
Toshihiko Shiraki
利彦 白木
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JTEKT Corp
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JTEKT Corp
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Priority to JP2008162703A priority Critical patent/JP2010002017A/en
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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
    • F16C33/7846—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 a gap between the annular disc and the inner 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
    • F16C19/04—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)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing, improved in grease leakage preventive performance. <P>SOLUTION: A side surface 8a inside in the axial direction of a seal housing groove 8 provided at the end of an inner ring 2 to house an inside diameter side edge of a non-contact seal 5 is a slant face inclined outward in the axial direction as it goes inward in the radial direction. The non-contact seal 6 is provided with a lip part 23 having a slant face 23b extending opposite to the slant face 8a of the seal housing groove 8. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

この発明は、転がり軸受に関し、より詳しくは、非接触シールを有しているグリース封入型の転がり軸受に関する。   The present invention relates to a rolling bearing, and more particularly to a grease-filled rolling bearing having a non-contact seal.

従来、グリース封入型の転がり軸受では、高速回転での使用に適するものとして、軸受の両端部に設けられた非接触シールによってグリースの洩れを防止するものが知られている（特許文献１など）。   2. Description of the Related Art Conventionally, grease-enclosed rolling bearings that are suitable for use at high-speed rotation are known in which grease leakage is prevented by non-contact seals provided at both ends of the bearing (eg, Patent Document 1). .

特許文献１のものでは、いわゆるリップ部が設けられていないが、グリース洩れ防止性能を向上させるために、図３に示すように、非接触シール(32)の内径側縁部にリップ部(33)を設けることにより、リップ部(33)の先端と内輪(31)外周面との間に形成された隙間によってもグリースの外部への漏れを防止しようとしたものが考えられている。
特開２００５−２３３２４９号公報 Although the so-called lip portion is not provided in Patent Document 1, in order to improve the grease leakage prevention performance, as shown in FIG. 3, the lip portion (33 ) To prevent leakage of grease to the outside also by a gap formed between the tip of the lip portion (33) and the outer peripheral surface of the inner ring (31).
JP 2005-233249 A

図３に示した転がり軸受によると、リップ部(33)によってグリース洩れ防止性能が向上するものの、後述するように、グリース洩れ防止性能が最適化されておらず、グリースが流動して、グリースが外部へ流出することがある。   According to the rolling bearing shown in FIG. 3, although the grease leakage prevention performance is improved by the lip portion (33), as described later, the grease leakage prevention performance is not optimized, the grease flows and the grease May flow out.

この発明の目的は、グリース洩れ防止性能を向上させた転がり軸受を提供することにある。   An object of the present invention is to provide a rolling bearing with improved grease leakage prevention performance.

この発明による転がり軸受は、内輪、外輪、両輪間に配置された複数の転動体および両輪端部間に配置された非接触シールを有している転がり軸受において、内輪端部に設けられて非接触シールの内径側縁部を収容するシール収容溝の軸方向内側の側面が、径方向の内方にいくにしたがって軸方向の外方に傾斜する傾斜面とされるとともに、非接触シールに、シール収容溝の傾斜面に対向してのびる傾斜面を有するリップ部が設けられていることを特徴とするものである。   A rolling bearing according to the present invention is a rolling bearing having an inner ring, an outer ring, a plurality of rolling elements disposed between both wheels, and a non-contact seal disposed between both wheel end portions. The side surface on the inner side in the axial direction of the seal housing groove that accommodates the inner diameter side edge portion of the contact seal is an inclined surface that is inclined outward in the axial direction as it goes inward in the radial direction. A lip portion having an inclined surface extending opposite to the inclined surface of the seal housing groove is provided.

非接触シールは、その内径側縁部が内輪端部に設けられたシール収容溝内に所定の間隙をおいて位置させられることで、ラビリンスシールを形成する。従来、シール収容溝の軸方向内側の側面は、軸方向に対して垂直の面とされていたのに対し、この発明による転がり軸受では、これが、径方向の内方にいくにしたがって軸方向の外方に傾斜する傾斜面とされている。また、従来、非接触シールのリップ部は、内輪の外径よりも大きい径を有する内周側円筒面と、円筒面の軸方向内方の端を先端面として径方向の外方にいくにしたがって軸方向の外方に傾斜する外周側傾斜面とを有していたのに対し、この発明による転がり軸受では、リップ部の内周側の面が、径方向の内方にいくにしたがって軸方向の外方に傾斜する傾斜面とされている。   A non-contact seal forms a labyrinth seal by positioning an inner diameter side edge portion within a seal receiving groove provided at an inner ring end portion with a predetermined gap. Conventionally, the side surface on the axially inner side of the seal receiving groove has been a surface perpendicular to the axial direction, whereas in the rolling bearing according to the present invention, the axial direction increases inward in the radial direction. The inclined surface is inclined outward. Further, conventionally, the lip portion of the non-contact seal has a radially outer side with the inner peripheral side cylindrical surface having a diameter larger than the outer diameter of the inner ring and the axially inner end of the cylindrical surface as a tip surface. Therefore, the rolling bearing according to the present invention has an outer peripheral inclined surface that is inclined outward in the axial direction. However, in the rolling bearing according to the present invention, the surface on the inner peripheral side of the lip portion moves toward the inner side in the radial direction. The inclined surface is inclined outward in the direction.

このようにすることで、非接触シールの内径側縁部とシール収容溝との間に、グリースが溜まる場所が無くなり、また、シール収容溝の傾斜面と非接触シールのリップ部との間に流出してきたグリースは、非接触シールの回転に伴う遠心力によって、径方向外方すなわち軸方向内方に押し戻されるので、グリースの外部への洩れが防止される。   By doing so, there is no place for grease to accumulate between the inner diameter side edge of the non-contact seal and the seal housing groove, and between the inclined surface of the seal housing groove and the lip of the non-contact seal. The grease that has flowed out is pushed back radially outward, that is, inward in the axial direction by the centrifugal force associated with the rotation of the non-contact seal, thereby preventing leakage of the grease to the outside.

非接触シールのリップ部内周側に形成される傾斜面は、例えば、ストレートテーパ面（断面が直線状）とされるが、グリースの溜まらない形状であれば、凸の曲面（断面凸円弧状）としてもよく、凸の曲面とストレートテーパ面とを組み合わせてもよい。   The inclined surface formed on the inner peripheral side of the lip portion of the non-contact seal is, for example, a straight taper surface (the cross section is linear). Alternatively, a convex curved surface and a straight tapered surface may be combined.

リップ部の先端径は、内輪の外径にほぼ等しいものとされるが、内輪の外径よりも小さい径とされることが好ましい。   The tip diameter of the lip portion is substantially equal to the outer diameter of the inner ring, but is preferably smaller than the outer diameter of the inner ring.

また、シール収容溝の傾斜面と非接触シールのリップ部内周側に形成される傾斜面とは、略平行とされるが、リップ部先端とシール収容溝の傾斜面との間の隙間をＣ、リップ部径方向内方端とシール収容溝の傾斜面との間の隙間をＢとし、Ｃ＞Ｂとされていることが好ましい。このようにすると、グリースが小さい隙間Ｂ側に移動しにくくなり、より一層グリース洩れ防止性能が向上する。Ｃより小さい隙間Ｂは、リップ部径方向内方端の近傍位置に設定することもできる。   Further, the inclined surface of the seal housing groove and the inclined surface formed on the inner peripheral side of the lip portion of the non-contact seal are substantially parallel, but the gap between the tip of the lip portion and the inclined surface of the seal housing groove is defined as C. The clearance between the radially inner end of the lip portion and the inclined surface of the seal housing groove is preferably B, and C> B. If it does in this way, it will become difficult to move grease to the small clearance gap B side, and grease leak prevention performance will improve further. The gap B smaller than C can also be set in the vicinity of the inner end in the lip portion radial direction.

この発明の転がり軸受によると、シール収容溝の軸方向内側の側面が、径方向の内方にいくにしたがって軸方向の外方に傾斜する傾斜面とされるとともに、非接触シールに、シール収容溝の傾斜面に対向してのびる傾斜面を有するリップ部が設けられているので、リップ部にグリースが溜まる場所が無く、また、遠心力が作用したときに、グリースには、これを軸受の内方に移動させる力が作用するので、グリースの洩れ性能が向上する。   According to the rolling bearing of this invention, the side surface on the axially inner side of the seal housing groove is an inclined surface that is inclined outward in the axial direction as it goes inward in the radial direction, and the seal housing is accommodated in the non-contact seal. Since the lip portion having an inclined surface extending opposite to the inclined surface of the groove is provided, there is no place for grease to collect in the lip portion, and when centrifugal force is applied, this is applied to the grease. Since the force to move inward acts, grease leakage performance is improved.

この発明の実施の形態を、以下図面を参照して説明する。以下の説明において、左右は、図１の左右をいうものとする。   Embodiments of the present invention will be described below with reference to the drawings. In the following description, the left and right refer to the left and right in FIG.

図１および図２は、この発明による転がり軸受を示している。   1 and 2 show a rolling bearing according to the present invention.

図１に示すように、転がり軸受(1)は、内輪(2)、外輪(3)、両輪(2)(3)間に配置された複数の玉（転動体）(4)、複数の玉(4)を保持する保持器(5)、および両輪(2)(3)端部間に配置された非接触シール(6)からなり、内部にグリース（図示略）が封入されている。   As shown in FIG. 1, the rolling bearing (1) is composed of an inner ring (2), an outer ring (3), a plurality of balls (rolling elements) (4) disposed between both wheels (2) and (3), and a plurality of balls. A cage (5) for holding (4) and a non-contact seal (6) disposed between the ends of both wheels (2) and (3) are filled with grease (not shown).

転がり軸受(1)は、左右対称とされており、内輪(2)の外周面および外輪(3)の内周面の軸方向の中央部には、それぞれ軌道溝(2a)(3a)が設けられている。また、外輪(3)の内周面の左右端部には、非接触シール(6)を取り付けるための環状のシール取付溝(7)が設けられており、内輪(2)の外周面の左右端部には、非接触シール(6)の内径側縁部を収容するシール収容溝(8)が設けられている。   The rolling bearing (1) is symmetrical, and a raceway groove (2a) (3a) is provided in the axial center of the outer peripheral surface of the inner ring (2) and the inner peripheral surface of the outer ring (3). It has been. In addition, annular seal mounting grooves (7) for mounting the non-contact seal (6) are provided at the left and right ends of the inner peripheral surface of the outer ring (3), and the left and right ends of the outer peripheral surface of the inner ring (2) are provided. A seal housing groove (8) for housing the inner diameter side edge of the non-contact seal (6) is provided at the end.

非接触シール(6)は、環状の芯金(11)と、芯金(11)に接着された弾性シール(12)とからなる。   The non-contact seal (6) includes an annular cored bar (11) and an elastic seal (12) bonded to the cored bar (11).

芯金(11)は、円板部(11a)と、円板部(11a)の外径側縁部において軸方向内方に直角に折り曲げられた外側折曲げ部(11b)と、円板部(11a)の内径側縁部において軸方向内方に鈍角に折り曲げられた内側折曲げ部(11c)とを有している。外側折曲げ部(11b)は、短円筒状をなし、その内径が外輪(3)の内径とほぼ等しくなされており、内側折曲げ部(11c)は、その内径が内輪(2)の外径とほぼ等しくなされている。   The core metal (11) includes a disc portion (11a), an outer bent portion (11b) bent at a right angle inward in the axial direction at an outer diameter side edge portion of the disc portion (11a), and a disc portion. An inner bent portion (11c) bent at an obtuse angle inward in the axial direction at an inner diameter side edge portion of (11a). The outer bent portion (11b) has a short cylindrical shape, and its inner diameter is substantially equal to the inner diameter of the outer ring (3), and the inner bent portion (11c) has an inner diameter of the outer ring (2). Is almost equal.

弾性シール(12)は、外側折曲げ部(11b)および内側折曲げ部(11c)と軸方向外側の面全面とを覆うように芯金(11)に接着されている。芯金(11)の外側折曲げ部(11b)を覆っている弾性シール(12)の外周縁部(21)は、弾性変形してシール取付溝(7)内に収められている。芯金(11)の内側折曲げ部(11c)を覆っている弾性シール(12)の部分は、芯金(11)の軸方向内側の面を基準にしてこれよりも軸方向外側にある内径側縁部(22)と、芯金(11)の軸方向内側の面を基準にしてこれよりも軸方向内方に突出したリップ部(23)とからなる。   The elastic seal (12) is bonded to the core metal (11) so as to cover the outer bent portion (11b) and the inner bent portion (11c) and the entire surface on the outer side in the axial direction. The outer peripheral edge portion (21) of the elastic seal (12) covering the outer bent portion (11b) of the core metal (11) is elastically deformed and stored in the seal mounting groove (7). The portion of the elastic seal (12) that covers the inner bent portion (11c) of the core metal (11) has an inner diameter that is on the axially outer side relative to the axially inner surface of the core metal (11). A side edge portion (22) and a lip portion (23) projecting inward in the axial direction with respect to the axially inner surface of the core metal (11).

図２に示すように、シール収容溝(8)は、内輪(2)の肩部に連なる軸方向内側の側面(8a)、これの軸方向外側に連なる底面(8b)、およびこれの軸方向外側に連なる軸方向外側の側面(8c)からなる。軸方向内側の側面(8a)は、径方向の内方にいくにしたがって軸方向の外方に傾斜する傾斜面とされており、底面(8b)は、円筒面、軸方向外側の側面(8c)は、径方向の外方にいくにしたがって軸方向の外方に傾斜する傾斜面とされている。   As shown in FIG. 2, the seal receiving groove (8) includes an axially inner side surface (8a) continuous with the shoulder portion of the inner ring (2), a bottom surface (8b) continuous with the axially outer side thereof, and an axial direction thereof. It consists of an axially outer side surface (8c) that continues to the outside. The axially inner side surface (8a) is an inclined surface that is inclined outward in the axial direction as it goes inward in the radial direction, and the bottom surface (8b) is a cylindrical surface, and the axially outer side surface (8c). ) Is an inclined surface that inclines outward in the axial direction as it goes outward in the radial direction.

弾性シール(12)の内径側縁部(22)は、シール収容溝(8)の底面(8b)および軸方向外側の側面(8c)に対向する内周面(22a)を有している。   The inner diameter side edge (22) of the elastic seal (12) has an inner peripheral surface (22a) facing the bottom surface (8b) and the axially outer side surface (8c) of the seal housing groove (8).

弾性シール(12)のリップ部(23)は、先端から径方向の外方にいくにしたがって軸方向の外方に傾斜する外周側傾斜面(23a)と、シール収容溝(8)の軸方向内側の傾斜面(8a)に対向しており先端から径方向の内方にいくにしたがって軸方向の外方に傾斜する内周側傾斜面(23b)とを有している。   The lip portion (23) of the elastic seal (12) includes an outer peripheral inclined surface (23a) that inclines outward in the axial direction as it goes radially outward from the tip, and an axial direction of the seal receiving groove (8). It has an inner inclined surface (23b) that faces the inner inclined surface (8a) and inclines outward in the axial direction as it goes radially inward from the tip.

リップ部(23)の先端の径は、内輪(2)の外径に対してＡで示す分だけ小さくなされている。リップ部(23)の内周側傾斜面(23b)の径方向内方端の径は、内径側縁部(22)の内周面(22a)の内径と等しくなされている。   The diameter of the tip of the lip portion (23) is made smaller by the amount indicated by A than the outer diameter of the inner ring (2). The diameter of the radially inner end of the inner peripheral inclined surface (23b) of the lip portion (23) is made equal to the inner diameter of the inner peripheral surface (22a) of the inner diameter side edge (22).

また、リップ部(23)先端とシール収容溝(8)の軸方向内側の傾斜面(8a)との間の隙間をＣ、リップ部(23)径方向内方端とシール収容溝(8)の軸方向内側の傾斜面(8a)との間の隙間をＢとして、隙間Ｂの位置では、内輪(2)と弾性シール(12)とが接触しない範囲で、弾性シール(12)が内輪(2)に近接するような値に設定されており、これにより、Ｃ＞Ｂとされている。   Further, the gap between the tip of the lip portion (23) and the inclined surface (8a) on the axially inner side of the seal housing groove (8) is C, and the radially inner end of the lip portion (23) and the seal housing groove (8). The clearance between the inner ring (2a) and the elastic seal (12) is within the range where the inner ring (2) and the elastic seal (12) do not contact at the position of the gap B, where B is the gap between the inclined surface (8a) on the inner side of the inner ring (8a). The value is set so as to be close to 2), so that C> B.

図３に示した従来の転がり軸受では、シール収容溝(35)の軸方向内側の側面(35a)は、軸方向に対して垂直の面とされており、また、非接触シール(32)のリップ部(33)は、内輪(31)の外径よりも大きい径を有する内周側円筒面(33a)と、円筒面(33a)の軸方向内方の端を先端として径方向の外方にいくにしたがって軸方向の外方に傾斜する外周側傾斜面(33b)とを有している。このため、リップ部(33)の内周側円筒面(33a)と内径側縁部(34)の軸方向内側の面とによって、凹所(36)が形成されており、この凹所(36)とこれに対向するシール収容溝(35)の面取り部(35b)との間は、グリースが溜まりやすい箇所となっており、この箇所まで流出してきたグリースは、軸受内部には戻れないので、その一部が外部へ洩れ出すことになる。   In the conventional rolling bearing shown in FIG. 3, the axially inner side surface (35a) of the seal receiving groove (35) is a surface perpendicular to the axial direction, and the non-contact seal (32) The lip portion (33) has an inner peripheral cylindrical surface (33a) having a diameter larger than the outer diameter of the inner ring (31) and an axially inner end of the cylindrical surface (33a). And an outer peripheral inclined surface (33b) that inclines outward in the axial direction. For this reason, a recess (36) is formed by the inner circumferential side cylindrical surface (33a) of the lip portion (33) and the axially inner surface of the inner diameter side edge portion (34), and this recess (36 ) And the chamfered portion (35b) of the seal receiving groove (35) opposite to this, it is a place where grease tends to accumulate, and the grease that has flowed out to this place cannot return to the inside of the bearing, Part of it will leak out.

これに対し、この発明の転がり軸受(1)によると、シール収容溝(8)の軸方向内側の傾斜面(8a)およびリップ部(23)の内周側傾斜面(23b)によって、グリースが溜まりやすい場所が無くなっている。また、リップ部(23)の内周側傾斜面(23b)によると、外輪(3)の回転によってリップ部(23)に作用した遠心力が、グリースを軸方向内方に押し戻すように作用する。したがって、外輪回転時のグリースの流れを円滑にして、グリース洩れ防止性能を向上させることができる。しかも、Ｃ＞Ｂとされていることで、この効果がより高められており、図３に示した従来のものに比べて、グリース洩れ防止性能が大幅に向上している。   In contrast, according to the rolling bearing (1) of the present invention, the grease is formed by the inclined surface (8a) on the axially inner side of the seal housing groove (8) and the inclined surface (23b) on the inner peripheral side of the lip portion (23). The place where it is easy to collect is gone. Further, according to the inner peripheral inclined surface (23b) of the lip portion (23), the centrifugal force acting on the lip portion (23) by the rotation of the outer ring (3) acts to push the grease back inward in the axial direction. . Therefore, it is possible to improve the grease leakage prevention performance by smoothing the flow of grease during rotation of the outer ring. In addition, since C> B, this effect is further enhanced, and the grease leakage prevention performance is greatly improved as compared with the conventional one shown in FIG.

図１は、この発明による転がり軸受の１実施形態を示す縦断面図である。FIG. 1 is a longitudinal sectional view showing an embodiment of a rolling bearing according to the present invention. 図２は、要部の拡大縦断面図である。FIG. 2 is an enlarged vertical sectional view of a main part. 図３は、従来の転がり軸受の図２に相当する縦断面図である。FIG. 3 is a longitudinal sectional view corresponding to FIG. 2 of a conventional rolling bearing.

符号の説明Explanation of symbols

(1) 転がり軸受
(2) 内輪
(3) 外輪
(4) 玉（転動体）
(6) 非接触シール
(8) シール収容溝
(8a) 軸方向内側の側面
(23) リップ部
(23b) 内周側傾斜面 (1) Rolling bearing
(2) Inner ring
(3) Outer ring
(4) Ball (rolling element)
(6) Non-contact seal
(8) Seal receiving groove
(8a) Axial inner side
(23) Lip part
(23b) Inner peripheral side inclined surface

Claims (2)

内輪、外輪、両輪間に配置された複数の転動体および両輪端部間に配置された非接触シールを有している転がり軸受において、
内輪端部に設けられて非接触シールの内径側縁部を収容するシール収容溝の軸方向内側の側面が、径方向の内方にいくにしたがって軸方向の外方に傾斜する傾斜面とされるとともに、非接触シールに、シール収容溝の傾斜面に対向してのびる傾斜面を有するリップ部が設けられていることを特徴とする転がり軸受。 In a rolling bearing having an inner ring, an outer ring, a plurality of rolling elements disposed between both wheels and a non-contact seal disposed between both wheel ends,
The axially inner side surface of the seal housing groove provided at the inner ring end portion for accommodating the inner side edge of the non-contact seal is an inclined surface that inclines outward in the axial direction as it goes inward in the radial direction. And a non-contact seal is provided with a lip portion having an inclined surface extending opposite to the inclined surface of the seal housing groove. リップ部の先端径は、内輪の外径よりも小さい径とされるとともに、リップ部先端とシール収容溝の傾斜面との間の隙間をＣ、リップ部径方向内方端とシール収容溝の傾斜面との間の隙間をＢとして、Ｃ＞Ｂとされていることを特徴とする請求項１の転がり軸受。   The tip diameter of the lip portion is smaller than the outer diameter of the inner ring, and the gap between the tip end of the lip portion and the inclined surface of the seal housing groove is C, and the lip portion radially inner end and the seal housing groove The rolling bearing according to claim 1, wherein a clearance between the inclined surfaces is B and C> B.
JP2008162703A 2008-06-23 2008-06-23 Rolling bearing Pending JP2010002017A (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012047248A (en) * 2010-08-26 2012-03-08 Nsk Ltd Rolling bearing
WO2015122099A1 (en) * 2014-02-17 2015-08-20 日本精工株式会社 Ball bearing with seal
DE102015220136A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf roller bearing
DE102015220138A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf roller bearing
DE102015220137A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf roller bearing
WO2017069225A1 (en) * 2015-10-23 2017-04-27 ジヤトコ株式会社 Sealed roller bearing and belt-type continuously-variable transmission

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JPS6449730U (en) * 1987-09-22 1989-03-28
JP2005226675A (en) * 2004-02-10 2005-08-25 Ntn Corp Sealed roller bearing
JP2005315313A (en) * 2004-04-28 2005-11-10 Ntn Corp Sealing structure of bearing
JP2007232089A (en) * 2006-03-01 2007-09-13 Ntn Corp Sealing structure of rolling bearing

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Publication number Priority date Publication date Assignee Title
JPS538455U (en) * 1976-07-07 1978-01-24
JPS59180016U (en) * 1983-05-20 1984-12-01 日本精工株式会社 Sealing device for rolling bearings
JPS6449730U (en) * 1987-09-22 1989-03-28
JP2005226675A (en) * 2004-02-10 2005-08-25 Ntn Corp Sealed roller bearing
JP2005315313A (en) * 2004-04-28 2005-11-10 Ntn Corp Sealing structure of bearing
JP2007232089A (en) * 2006-03-01 2007-09-13 Ntn Corp Sealing structure of rolling bearing

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012047248A (en) * 2010-08-26 2012-03-08 Nsk Ltd Rolling bearing
WO2015122099A1 (en) * 2014-02-17 2015-08-20 日本精工株式会社 Ball bearing with seal
KR20160097280A (en) * 2014-02-17 2016-08-17 닛본 세이고 가부시끼가이샤 Ball bearing with seal
CN106030135A (en) * 2014-02-17 2016-10-12 日本精工株式会社 Ball bearing with seal
JPWO2015122099A1 (en) * 2014-02-17 2017-03-30 日本精工株式会社 Ball bearing with seal
DE102015220136A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf roller bearing
DE102015220138A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf roller bearing
DE102015220137A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf roller bearing
WO2017069225A1 (en) * 2015-10-23 2017-04-27 ジヤトコ株式会社 Sealed roller bearing and belt-type continuously-variable transmission

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