JP2008163989A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
JP2008163989A
JP2008163989A JP2006352177A JP2006352177A JP2008163989A JP 2008163989 A JP2008163989 A JP 2008163989A JP 2006352177 A JP2006352177 A JP 2006352177A JP 2006352177 A JP2006352177 A JP 2006352177A JP 2008163989 A JP2008163989 A JP 2008163989A
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Japan
Prior art keywords
seal member
peripheral portion
outer peripheral
locking groove
seal
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Pending
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JP2006352177A
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Japanese (ja)
Inventor
Takahiro Kanemoto
崇広 金本
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2006352177A priority Critical patent/JP2008163989A/en
Publication of JP2008163989A publication Critical patent/JP2008163989A/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
    • F16C33/7816—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
    • 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
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F16C43/045—Mounting or replacing seals
    • 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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing for improving the performance of incorporating a seal member into a locking groove. <P>SOLUTION: Rolling elements 3 are laid between both raceways 5, 6 of an inner ring 1 and an outer ring 2, and the locking groove 8 is formed in the inner peripheral face of the outer ring 2 facing a seal groove 7 formed in the side of the raceway 5 of the inner ring 1. An outer peripheral portion 9 of the seal member 4 is mounted in the locking groove 8 with a required press-in allowance. A thickness A in the axial direction of the outer peripheral portion 9 is 1.0-2.5 times a width B in the radial direction of an elastic body 11 on the outer periphery side of a core metal 10. Thus, the rigidity of the outer peripheral portion 9 of the seal member 4 is higher than conventional one to produce greater restoring force on elastic deformation. During mounting the seal member 4 when the press-in allowance 18 of the outer peripheral portion 9 is elastically deformed outward to the bearing, the great restoring force restores the elastically deformed press-in allowance 18 into the original condition, therefore improving the performance of incorporating the seal member 4 into the locking groove 8. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

この発明は、電磁クラッチ、プーリ等の各種機械装置の回転軸支持部に組み込まれる転がり軸受に関するものである。   The present invention relates to a rolling bearing incorporated in a rotating shaft support portion of various mechanical devices such as an electromagnetic clutch and a pulley.

一般に、各種機械装置の回転軸支持部には、軸受内部のグリースが外部に漏れるのを防止するとともに、外部からの異物の進入を防止するために密封型転がり軸受が採用されている。   In general, a sealing type rolling bearing is employed in a rotating shaft support portion of various mechanical devices in order to prevent grease inside the bearing from leaking to the outside and to prevent foreign matter from entering from the outside.

この密封型転がり軸受は、内輪および外輪の両軌道の間に複数の転動体を介在させ、内輪の軌道の両側方に周方向のシール溝が形成されるとともに、この各シール溝に対向する外輪の内周面に係止溝が形成される。この係止溝に弾性体を芯金で補強した環状のシール部材が装着され、このシール部材の内周部に設けられたシールリップを内輪のシール溝の側壁に摺接させたものである。このシールリップの摺接により、軸受内部のグリースが外部に漏れるのを防止するとともに、外部からの異物の進入を防止している（特許文献１ 図１、図２ 参照）。
特開２００５−１８０５７５号公報 In this sealed rolling bearing, a plurality of rolling elements are interposed between both races of the inner ring and the outer ring, and circumferential seal grooves are formed on both sides of the race of the inner ring, and the outer ring facing each seal groove. A locking groove is formed on the inner peripheral surface of the. An annular seal member in which an elastic body is reinforced with a metal core is attached to the locking groove, and a seal lip provided on the inner peripheral portion of the seal member is brought into sliding contact with the side wall of the seal groove of the inner ring. The sliding contact of the seal lip prevents the grease inside the bearing from leaking to the outside and prevents the entry of foreign matter from the outside (see Patent Document 1 FIGS. 1 and 2).
JP 2005-180575 A

上記転がり軸受は、そのシール部材の外周部が、係止溝にその溝壁との間で所要の圧入代をもって装着される。この圧入代は、前記シール部材の外周部の形状と、係止溝の形状とによって規定されるが、シール部材の圧入代が不十分であれば、シール部材が係止溝に対して安定して組み込まれず、シールリップによるシール性に悪影響を及ぼすおそれがあった。そのため、シール部材の外周部の形状を規定して十分な圧入代を形成することにより、シールリップによるシール性を確保している。   In the rolling bearing, the outer peripheral portion of the seal member is attached to the locking groove with a required press-fitting allowance between the locking wall and the groove wall. This press-fitting allowance is defined by the shape of the outer peripheral portion of the seal member and the shape of the locking groove. If the press-fitting allowance of the seal member is insufficient, the seal member is stable with respect to the locking groove. There was a risk of adversely affecting the sealing performance of the seal lip. Therefore, the sealing performance by the seal lip is secured by defining the shape of the outer peripheral portion of the seal member and forming a sufficient press-fitting allowance.

通常、上記転がり軸受のシール部材３１は、図４に示すように、係止溝３２に装着する際に、その外周部３３が係止溝３２の外輪端面側の肩部３４に押し付けられ、この肩部３４からの反力を受けて軸受外向きに弾性変形しながら組み込まれる。しかし、上述のように、外周部３３が係止溝３２との間で所要の圧入代をもって形成されても、外周部３３の軸方向の厚みＡが、シール部材３１の外周部３３から芯金の外周部までの径方向の幅Ｂよりも小さければ（例えば、Ａ／Ｂ＝０．８であれば）、シール部材３１の外周部３３の剛性が低くなり、得られる復元力が小さくなる。このため、弾性変形した外周部３３が元の状態に戻らず前記肩部３４に捲くれて残ることがあった（図４の一点鎖線参照）。前記外周部３３の一部が捲くれて残れば、圧入締め代が小さくなるとともに係止溝３２に対するシール部材３１の組み込み位置が不安定になり、シールリップによるシール性の確保が難しいという問題があった。   Normally, when the sealing member 31 of the rolling bearing is mounted in the locking groove 32 as shown in FIG. 4, the outer peripheral portion 33 is pressed against the shoulder portion 34 on the outer ring end face side of the locking groove 32. In response to the reaction force from the shoulder 34, the bearing is incorporated while elastically deforming outward. However, as described above, even if the outer peripheral portion 33 is formed with the required press-fitting allowance between the outer peripheral portion 33 and the locking groove 32, the axial thickness A of the outer peripheral portion 33 is reduced from the outer peripheral portion 33 of the seal member 31 to the cored bar. If the width B is smaller than the radial width B to the outer peripheral portion (for example, if A / B = 0.8), the rigidity of the outer peripheral portion 33 of the seal member 31 is reduced, and the resulting restoring force is reduced. For this reason, the elastically deformed outer peripheral portion 33 may not be returned to the original state but may remain on the shoulder portion 34 (see the dashed line in FIG. 4). If a part of the outer peripheral portion 33 is left over, there is a problem that the press-fit tightening margin becomes small and the position where the seal member 31 is assembled with the locking groove 32 becomes unstable, and it is difficult to ensure the sealing performance by the seal lip. there were.

そこで、シール部材の係止溝に対する組み込み性を向上させた転がり軸受を提供することを課題とする。   Accordingly, an object of the present invention is to provide a rolling bearing with improved assemblability with respect to the locking groove of the seal member.

上記の課題を解決するために、この発明は、シール部材の外周部を径方向の厚みよりも軸方向の厚みを厚くしたのである。   In order to solve the above problems, the present invention is such that the outer peripheral portion of the seal member is thicker in the axial direction than in the radial direction.

このようにすれば、上記シール部材の外周部は、その剛性が高くなり、大きい復元力が得られるので、シール部材の係止溝への装着時に外周部が軸受外向きに弾性変形しても、その弾性変形した外周部が元の状態に戻り、係止溝内に引き込まれて収まる。   In this way, the outer peripheral portion of the seal member has a high rigidity and a large restoring force is obtained. Therefore, even when the outer peripheral portion is elastically deformed outwardly of the bearing when the seal member is mounted in the locking groove. The elastically deformed outer peripheral portion returns to the original state and is retracted into the locking groove.

この発明は、以上のように、シール部材の係止溝への装着時、シール部材の外周部が係止溝に収まるので、シール部材が係止溝に対して安定して取り付けられるとともに、組み込み性を向上させることができる。   As described above, according to the present invention, when the seal member is mounted in the locking groove, the outer peripheral portion of the seal member is accommodated in the locking groove. Can be improved.

この発明の実施形態は、内輪および外輪の両軌道間に転動体が介在され、前記外輪の軌道の側方に係止溝が形成され、この係止溝に弾性体を芯金で補強したシール部材の外周部が所要の圧入代をもって装着され、前記係止溝に対向し前記内輪に形成されたシール溝に、前記シール部材の内周部に設けられたシールリップが摺接する転がり軸受において、前記シール部材の外周部の軸方向の厚みが、前記シール部材の外周部から芯金の外周部までの径方向の幅に対して、１．０〜２．５倍に形成された構成を採用することができる。   In an embodiment of the present invention, a rolling element is interposed between both races of the inner ring and the outer ring, a locking groove is formed on a side of the track of the outer ring, and a seal in which an elastic body is reinforced with a cored bar. In the rolling bearing in which the outer peripheral portion of the member is mounted with a required press-fitting allowance, and the seal lip provided on the inner peripheral portion of the seal member is in sliding contact with the seal groove formed in the inner ring facing the locking groove, The axial thickness of the outer periphery of the seal member is configured to be 1.0 to 2.5 times the radial width from the outer periphery of the seal member to the outer periphery of the cored bar. can do.

この構成において、上記シール部材は、その外周部の軸受内側寄りに面取りされたガイド部が形成された構成を採用することができる。このガイド部は、角が面取りされたものなので、上記シール部材を係止溝に装着する際、係止溝と外輪端部との間に形成された肩部に前記ガイド部が押し付けられると、このガイド部に沿ってシール部材の外周部が係止溝へ案内される。   In this configuration, the seal member may employ a configuration in which a chamfered guide portion is formed on the outer periphery of the seal member toward the inside of the bearing. Since this guide portion has a chamfered corner, when the seal member is attached to the locking groove, when the guide portion is pressed against the shoulder formed between the locking groove and the outer ring end portion, The outer peripheral portion of the seal member is guided to the locking groove along this guide portion.

以下、この発明の実施例を図１〜図３に基づいて説明する。この実施例の転がり軸受は、図１、図２に示すように、外周面に軌道５を有する内輪１と、内周面に軌道６を有する外輪２と、内外輪１、２の両軌道５、６の間に介在された複数の転動体３と、内輪１および外輪２の軸方向両端面に装着され、内外輪１、２の間を封止する環状のシール部材４とから構成される。   Embodiments of the present invention will be described below with reference to FIGS. As shown in FIGS. 1 and 2, the rolling bearing of this embodiment includes an inner ring 1 having a raceway 5 on an outer peripheral surface, an outer ring 2 having a raceway 6 on an inner peripheral surface, and both raceways 5 of inner and outer rings 1 and 2. , 6, and a plurality of rolling elements 3, and annular seal members 4 that are attached to both axial end surfaces of the inner ring 1 and the outer ring 2 and seal between the inner and outer rings 1, 2. .

上記内輪１の軌道５の両側方に周方向のシール溝７が形成され、この各シール溝７に向かい合う外輪２の内周面に係止溝８が形成される。この係止溝８と外輪２の端部との間に肩部１６が形成され、前記係止溝８に上記シール部材４の外周部９が所要の圧入代をもって装着される。   A circumferential seal groove 7 is formed on both sides of the raceway 5 of the inner ring 1, and a locking groove 8 is formed on the inner peripheral surface of the outer ring 2 facing each seal groove 7. A shoulder 16 is formed between the locking groove 8 and the end of the outer ring 2, and the outer peripheral portion 9 of the seal member 4 is attached to the locking groove 8 with a required press-fitting allowance.

上記係止溝８は、図２に示すように、外輪２の軌道６側の溝壁１４（以下、軌道側溝壁１４という。）と、底面１５と、係止溝８と外輪２の端部との間に形成される肩部１６側の溝壁１７（以下、肩部側溝壁１７という。）とから形成され、この肩部側溝壁１７が、軸方向外向きの縮径する向きに傾斜し、前記肩部１６の外周面と連続して形成される。   As shown in FIG. 2, the locking groove 8 includes a groove wall 14 on the track 6 side of the outer ring 2 (hereinafter referred to as a track-side groove wall 14), a bottom surface 15, an end of the locking groove 8 and the outer ring 2. And a groove wall 17 on the shoulder 16 side (hereinafter referred to as a shoulder-side groove wall 17) formed between the shoulder-side groove wall 17 and the shoulder-side groove wall 17 is inclined in the direction of reducing the diameter outward in the axial direction. And formed continuously with the outer peripheral surface of the shoulder 16.

上記係止溝８に装着されるシール部材４は、合成ゴム等からなる弾性体１１を芯金１０により補強したものであり、その内周部の弾性体１１の部分にその肉厚が薄い支持部１２が形成される。この支持部１２の内周側の先端部にはシールリップ１３が設けられ、このシールリップ１３が、上記シール溝７の軌道５側の側壁に摺接する。これにより、軸受内部のグリースがシール溝７に漏出することを防止するとともに、外部からの異物や泥水などの軸受内部への侵入を防止する。   The seal member 4 mounted in the locking groove 8 is obtained by reinforcing an elastic body 11 made of synthetic rubber or the like with a cored bar 10 and supporting the thin elastic member 11 on the inner peripheral portion thereof. Part 12 is formed. A seal lip 13 is provided at the inner peripheral end of the support portion 12, and the seal lip 13 is in sliding contact with the side wall of the seal groove 7 on the track 5 side. This prevents grease inside the bearing from leaking into the seal groove 7 and prevents foreign matter and muddy water from entering the bearing.

また、上記シール部材４は、その外周部９の弾性体１１部分の外径Ｒ１が、上記係止溝８の底面１５の内径Ｒ２よりも小さく、外輪２の肩部１６の内径Ｒ３よりも大きく、すなわち、Ｒ３＜Ｒ１＜Ｒ２となるように形成されたものである。このようにシール部材４を形成すれば、後述する圧入代１８が係止溝８の肩部側溝壁１７により押し付けられる。   Further, the outer diameter R1 of the elastic body 11 portion of the outer peripheral portion 9 of the seal member 4 is smaller than the inner diameter R2 of the bottom surface 15 of the locking groove 8, and larger than the inner diameter R3 of the shoulder portion 16 of the outer ring 2. That is, it is formed so that R3 <R1 <R2. If the seal member 4 is formed in this way, a press-fitting allowance 18 described later is pressed by the shoulder-side groove wall 17 of the locking groove 8.

また、前記シール部材４を径方向の断面形状で見た場合において、シール部材４の外周部９の軸受内側寄りにガイド部１９が形成される。このガイド部１９は、外周部９の軸受内側寄りの角部分を面取りして形成したので、シール部材４を係止溝８に装着する際、係止溝８の肩部１６に前記ガイド部１９が押し付けられると、このガイド部１９に沿ってシール部材４の外周部９が係止溝８へ案内される。   Further, when the seal member 4 is viewed in a radial cross-sectional shape, a guide portion 19 is formed on the inner side of the bearing of the outer peripheral portion 9 of the seal member 4. Since the guide portion 19 is formed by chamfering the corner portion of the outer peripheral portion 9 closer to the inside of the bearing, when the seal member 4 is attached to the locking groove 8, the guide portion 19 is placed on the shoulder portion 16 of the locking groove 8. Is pressed, the outer peripheral portion 9 of the seal member 4 is guided to the locking groove 8 along the guide portion 19.

さらに、上記シール部材４の外周部９の、係止溝８の肩部側溝壁１７よりも軸受外側部分には圧入代１８が形成される。シール部材４の外周部９が係止溝８に装着されると、前記圧入代１８が係止溝８の肩部側溝壁１７により押し付けられ弾性変形し、肩部側溝壁１７から受ける反力で外周部９が係止溝８の軌道側溝壁１４に押し付けられる。これにより、シール部材４が係止溝８に圧入により装着される。   Further, a press-fitting allowance 18 is formed in a portion outside the bearing of the outer peripheral portion 9 of the seal member 4 rather than the shoulder side groove wall 17 of the locking groove 8. When the outer peripheral portion 9 of the seal member 4 is mounted in the locking groove 8, the press-fitting allowance 18 is pressed and elastically deformed by the shoulder side groove wall 17 of the locking groove 8, and the reaction force received from the shoulder side groove wall 17 The outer peripheral portion 9 is pressed against the track-side groove wall 14 of the locking groove 8. As a result, the seal member 4 is fitted into the locking groove 8 by press fitting.

上記シール部材４の外周部９は、図２に示すように、その軸方向の厚みＡが、芯金１０よりも外周部の弾性体１１の径方向の幅Ｂに対して１．０〜２．５倍（例えば、図２では、１．２倍）の大きさに形成される。   As shown in FIG. 2, the outer peripheral portion 9 of the sealing member 4 has an axial thickness A of 1.0 to 2 with respect to the radial width B of the elastic body 11 at the outer peripheral portion rather than the core metal 10. The size is 5 times (for example, 1.2 times in FIG. 2).

上記のようにシール部材４の外周部９を形成したのは、前記厚みＡが前記幅Ｂの１．０倍未満であれば、前記シール部材４の外周部９の剛性が低く、得られる復元力が小さくなるため、従来のシール部材のように、弾性変形した外周部が元の状態に戻らず前記肩部に捲くれて残るおそれがあるからである。また、前記厚みＡが前記幅Ｂの２．５倍を超えると、加硫性の悪化(偏肉や欠肉)、離型性、精度確保困難といった品質上の問題や、金型部品点数の増加によるコストアップが発生するからである。   The reason why the outer peripheral portion 9 of the seal member 4 is formed as described above is that if the thickness A is less than 1.0 times the width B, the rigidity of the outer peripheral portion 9 of the seal member 4 is low, and the resulting restoration is obtained. This is because, since the force is reduced, the elastically deformed outer peripheral portion may not be restored to the original state and may remain over the shoulder portion like a conventional seal member. Further, if the thickness A exceeds 2.5 times the width B, quality problems such as deterioration of vulcanizability (uneven thickness and lack of thickness), releasability and difficulty in ensuring accuracy, and the number of mold parts This is because the cost increases due to the increase.

上記のように形成されるシール部材４の外周部９は、従来の場合と比較して剛性が高くなるため、弾性変形に対して大きい復元力が得られる。外周部９の復元力が大きくなると、図３に示すように、シール部材４を係止溝８に装着する際、外周部９の圧入代１８が軸受外向きに弾性変形しても、その弾性変形した圧入代１８が元の状態に戻り、係止溝８に収まる。係止溝８内に圧入代１８が収まることにより、シール部材４が係止溝８に対して安定した状態で装着されるとともに、シール部材４の組み込み性を向上させることができる。   Since the outer peripheral portion 9 of the seal member 4 formed as described above has higher rigidity than the conventional case, a large restoring force can be obtained against elastic deformation. When the restoring force of the outer peripheral portion 9 is increased, as shown in FIG. 3, even when the press-fitting allowance 18 of the outer peripheral portion 9 is elastically deformed outwardly when the seal member 4 is mounted in the locking groove 8, the elasticity The deformed press-fitting allowance 18 returns to the original state and fits in the locking groove 8. By fitting the press-fitting allowance 18 into the locking groove 8, the seal member 4 is mounted in a stable state with respect to the locking groove 8, and the assemblability of the seal member 4 can be improved.

実施例の転がり軸受を示す断面図Sectional drawing which shows the rolling bearing of an Example 同上のシール部材を示す断面拡大図Cross-sectional enlarged view showing the sealing member 同上のシール部材を係止溝に装着した状態を示す断面拡大図Cross-sectional enlarged view showing a state in which the sealing member is mounted in the locking groove. 従来の転がり軸受のシール部材を係止溝に装着した状態を示す断面拡大図Sectional enlarged view showing a state in which a seal member of a conventional rolling bearing is mounted in a locking groove

符号の説明Explanation of symbols

１ 内輪
２ 外輪
３ 転動体
４ シール部材
５ 内輪軌道
６ 外輪軌道
７ シール溝
８ 係止溝
９ 外周部
１０ 芯金
１１ 弾性体
１２ 支持部
１３ シールリップ
１４ 軌道側溝壁
１５ 底面
１６ 肩部
１７ 肩部側溝壁
１８ 圧入代
１９ ガイド部
３１ 内周面
３２ 係止溝
３３ 外周部
３４ 肩部 DESCRIPTION OF SYMBOLS 1 Inner ring 2 Outer ring 3 Rolling body 4 Seal member 5 Inner ring track 6 Outer ring track 7 Seal groove 8 Locking groove 9 Outer peripheral part 10 Core 11 Elastic body 12 Support part 13 Seal lip 14 Track side groove wall 15 Bottom face 16 Shoulder part 17 Shoulder part Side groove wall 18 Press-fitting allowance 19 Guide part 31 Inner peripheral surface 32 Locking groove 33 Outer peripheral part 34 Shoulder part

Claims (2)

内輪（１）および外輪（２）の両軌道（５）、（６）間に転動体（３）が介在され、前記外輪（２）の軌道（６）の側方に係止溝（８）が形成され、この係止溝（８）に弾性体（１１）を芯金（１０）で補強したシール部材（４）の外周部が所要の圧入代をもって装着され、前記係止溝（８）に対向し前記内輪（１）に形成されたシール溝（７）に、前記シール部材（４）の内周部に設けられたシールリップ（１３）が摺接する転がり軸受において、
上記シール部材（４）の外周部の軸方向の厚みＡが、上記シール部材（４）の外周部から芯金（１０）の外周部までの径方向の幅Ｂに対して、１．０〜２．５倍に形成されたことを特徴とする転がり軸受。 A rolling element (3) is interposed between the raceways (5) and (6) of the inner ring (1) and the outer race (2), and a locking groove (8) is formed on the side of the raceway (6) of the outer race (2). The outer peripheral portion of the sealing member (4) in which the elastic body (11) is reinforced with the core metal (10) is attached to the locking groove (8) with a required press-fitting allowance, and the locking groove (8) In a rolling bearing in which a seal lip (13) provided on an inner peripheral portion of the seal member (4) is in sliding contact with a seal groove (7) formed in the inner ring (1) opposite to
The axial thickness A of the outer peripheral portion of the seal member (4) is 1.0 to the radial width B from the outer peripheral portion of the seal member (4) to the outer peripheral portion of the metal core (10). A rolling bearing characterized by being formed 2.5 times. 上記シール部材（４）は、その外周部の軸受内側寄りに面取りされたガイド部（１９）が形成されたことを特徴する請求項1に記載の転がり軸受。   The rolling bearing according to claim 1, wherein the seal member (4) is formed with a guide portion (19) chamfered on the outer periphery of the seal member (4) toward the inside of the bearing.
JP2006352177A 2006-12-27 2006-12-27 Rolling bearing Pending JP2008163989A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2006352177A JP2008163989A (en) 2006-12-27 2006-12-27 Rolling bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006352177A JP2008163989A (en) 2006-12-27 2006-12-27 Rolling bearing

Publications (1)

Publication Number Publication Date
JP2008163989A true JP2008163989A (en) 2008-07-17

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Family Applications (1)

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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011155025A1 (en) 2010-06-08 2011-12-15 Ntn株式会社 Rubber composition and molded rubber products

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011155025A1 (en) 2010-06-08 2011-12-15 Ntn株式会社 Rubber composition and molded rubber products
US9012551B2 (en) 2010-06-08 2015-04-21 Ntn Corporation Rubber composition and molded rubber products

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