JP2004197790A - Double row rolling bearing - Google Patents

Double row rolling bearing Download PDF

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Publication number
JP2004197790A
JP2004197790A JP2002364939A JP2002364939A JP2004197790A JP 2004197790 A JP2004197790 A JP 2004197790A JP 2002364939 A JP2002364939 A JP 2002364939A JP 2002364939 A JP2002364939 A JP 2002364939A JP 2004197790 A JP2004197790 A JP 2004197790A
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JP
Japan
Prior art keywords
retaining ring
snap ring
locating snap
annular groove
ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2002364939A
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Japanese (ja)
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JP4262974B2 (en
Inventor
Tatsuya Omoto
達也 大本
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2002364939A priority Critical patent/JP4262974B2/en
Publication of JP2004197790A publication Critical patent/JP2004197790A/en
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Publication of JP4262974B2 publication Critical patent/JP4262974B2/en
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Classifications

    • 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
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To prevent the tripping of a locating snap ring while securing workability, in assembly work of a double row rolling bearing in which two inner races are fastened with the locating snap ring. <P>SOLUTION: The C-shaped locating snap ring 6 is fitted into a recessed annular groove 7 formed to cut across two inner races 2, 3. A diameter of the locating snap ring 6 is reduced until its opening part is closed (its inside diameter becomes d<SB>0</SB>-δ<SB>0</SB>/π), where the inside diameter of the locating snap ring 6 is d<SB>0</SB>and width of the opening part is δ<SB>0</SB>. Height H in section of the locating snap ring 6 is set so that there is no part of the locating snap ring tripping from the annular groove 7 even in a state where the locating snap ring is largely shifted from axial centers of the inner races 2, 3. Therefore, without change in dimension of the locating snap ring causing the lowering of the workability, the tripping of the locating snap ring is prevented. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
この発明は、２個の内輪を止め輪で締結した複列転がり軸受に関する。
【０００２】
【従来の技術】
内外輪間に転動体を２列に組み込んだ複列転がり軸受には、それぞれ１列の軌道面を有する２個の内輪を端面どうしで突き合わせて締結したものがある。
【０００３】
この種の複列転がり軸受における内輪の締結構造は、本発明の実施形態である図１に示すように、各内輪２、３の突き合わせ端近傍の内径面にＬ字形断面の凹部２ｂ、３ｂを環状に設け、これらの凹部２ｂ、３ｂを対向させることにより両内輪２、３に跨がって形成される凹形断面の環状溝７に、断面が凹形の止め輪６を嵌め込むようにしたものが多い。止め輪６は、周方向の一箇所に開口部が形成されたＣ字形のもので、開口部を狭めた状態で環状溝７に嵌め込まれており、その拡径方向の弾性復元力により両内輪２、３を一体化している（例えば、特許文献１、２参照。）。
【０００４】
【特許文献１】
特開２００１−２８９２５５号公報
【特許文献２】
実開平３−２０７２５号公報
【０００５】
【発明が解決しようとする課題】
上述した内輪締結構造の複列転がり軸受を軸に組み込む際には、止め輪で締結されている２個の内輪のうちの一方の外側端部を軸端部に嵌め込んだときに、内輪と軸との間の隙間により両内輪の軸心がわずかに傾いた状態となり、両内輪を周方向に揺動させながら軸に押し込んでいくことが必要となる場合が多い。
【０００６】
このとき、軸の表面性状や軸に対する内輪の傾き状態によっては、軸と一方の内輪との摩擦力が両内輪間の摩擦力よりも大きくなって、両内輪の間に相対的な周方向位置のずれが生じる。両内輪の周方向位置がずれると、止め輪は、周方向の剪断力を受けて縮径することによりその周方向の一部が環状溝から外れた状態となり、軸端面が当接してスラスト荷重を受けたときに全体が環状溝から外れてしまうことがある。止め輪外れが発生すると、途中まで押し込んだ両内輪を引き戻して止め輪を嵌め直さざるをえず、組込作業の能率が大きく低下する。
【０００７】
これに対して、止め輪の断面係数を大きくして、環状溝に嵌め込まれた状態での拡径方向の弾性復元力を大きくすれば、両内輪の相対的な周方向位置ずれを生じにくくすることができる。しかし、この方法を採用すると、止め輪を内輪内周側に装着する際に大きな縮径力が必要となり、作業性が大幅に悪化する。
【０００８】
そこで、この発明の課題は、２個の内輪を止め輪で締結した複列転がり軸受の組込作業において、作業性を確保しつつ、止め輪外れを防止することである。
【０００９】
【課題を解決するための手段】
上記の課題を解決するため、この発明は、止め輪がその開口部が閉じるまで縮径しても両内輪の環状溝から外れる部分が生じないように、止め輪の断面高さを規定したのである。これにより、止め輪が最も縮径した状態で両内輪を軸に押し込んでいっても、止め輪は軸に押し拡げられて全体が環状溝に嵌まり込むようになり、止め輪外れを発生しにくくすることができる。
【００１０】
具体的には、２個の内輪を端面どうしで突き合わせ、両内輪の突き合わせ端近傍の内径面に環状に設けたＬ字形断面の凹部を対向させて、両内輪に跨がる凹形断面の環状溝を形成し、この環状溝に断面が凹形で周方向の一箇所に開口部を有する止め輪を嵌め込むことにより、両内輪を一体に締結した複列転がり軸受において、前記止め輪の断面高さＨを、前記内輪の内径ｄと、止め輪の内径ｄ0 および開口部の幅δ0 とに基づいて、下記（１）式が成立するように設定したのである。
【００１１】
Ｈ＞ｄ−ｄ0 ＋δ0 ／π ・・・ （１）
上記（１）式は、開口部が閉じるまで縮径した状態（内径：ｄ0 −δ0 ／π）の止め輪が、内輪の軸心からずれて、周方向のある位置で完全に環状溝内に嵌まり込んでいる（止め輪と内輪の内径面が一致している）ときに、周方向の反対側の位置で少なくとも外周縁部が環状溝内に入るという条件から導かれる。
【００１２】
【発明の実施の形態】
以下、図１乃至図３に基づき、この発明の実施形態を説明する。図１は、この複列転がり軸受を軸Ａに組み込んでいる途中の状態を示す。この軸受は、２列の軌道面１ａ、１ｂを有する外輪１と、外輪１の各軌道面１ａ、１ｂのそれぞれと対向する軌道面２ａ、３ａを有する２個の内輪２、３と、互いに対向する軌道面１ａ、２ａおよび１ｂ、３ａ間で転動する２列のテーパころ４と、各列のテーパころ４を保持する保持器５とで基本的に構成されている。２個の内輪２、３は、端面どうしで突き合わされた状態で、その内周側に装着された止め輪６によって一体に締結されている。
【００１３】
前記端面どうしで突き合わされた両内輪２、３の締結構造は、前述したように、各内輪２、３の突き合わせ端近傍の内径面にＬ字形断面の凹部２ｂ、３ｂを環状に設け、これらの凹部２ｂ、３ｂを対向させることにより両内輪２、３に跨がる凹形断面の環状溝７を形成し、この環状溝７に断面が凹形の止め輪６を嵌め込んでいる。止め輪６は、図２（ａ）に実線で示すように、周方向の一箇所に開口部が形成されたＣ字形のもので、開口部を狭めた状態で環状溝７に嵌め込まれており、その拡径方向の弾性復元力により両内輪２、３を一体化している。
【００１４】
前記止め輪６の寸法は、図２（ａ）、（ｂ）に示すように、その内径をｄ0 、開口部の幅をδ0 、断面高さをＨとし、内輪２、３の内径をｄとするとき、下記（１）式が成立するように設定されている。なお、この実施形態では、図１に示したように、両内輪２、３の環状溝７縁部に、軸受組立時に環状溝７への止め輪６の嵌め込みをスムーズにするためのテーパ部が設けられており、各内輪２、３の内周側円筒面の直径にこのテーパ部の深さの分を加えて、止め輪寸法設定用の内輪内径ｄとしている。
【００１５】
Ｈ＞ｄ−ｄ0 ＋δ0 ／π ・・・ （１）
この軸受は、以上の構成であり、図１に示したように一方の内輪３の外側端部を軸Ａ端部に嵌め、両内輪２、３を周方向に揺動させながら軸Ａに組み込んでいくときに、両内輪２、３の相対的な周方向位置のずれにより、止め輪６が周方向の剪断力を受けて、図２（ａ）に点線で示すように、その開口部が閉じる（内径がｄ0 −δ0 ／πとなる）まで縮径する可能性がある。
【００１６】
しかし、図３に示すように、開口部が閉じるまで縮径した状態の止め輪６が、内輪２、３の軸心からずれて周方向のある位置で完全に環状溝７内に嵌まり込む（止め輪６と内輪２、３の内径面が一致する）場合でも、止め輪６は、断面高さＨが上記（１）式を満足しているため、周方向の反対側の位置で少なくとも外周縁部が環状溝７内に入る。この状態で両内輪２、３を軸Ａに押し込んでいけば、止め輪６は軸Ａで押し拡げられて全体が環状溝７に嵌まり込む。
【００１７】
すなわち、この軸受では、軸への組込作業中に止め輪が周方向の剪断力を受けて縮径しても、止め輪は周方向のどの位置でも環状溝から外れることがなく、止め輪外れを防止することができる。なお、軸受組立時には、止め輪をコイルばね状に変形させることにより、不都合なく内輪内周側に装着することができる。
【００１８】
なお、上記（１）式は、軸受に装着された止め輪がその開口部が閉じるまで縮径しても環状溝から外れる部分が生じないように、止め輪寸法を規定したものなので、（１）式が成立するように止め輪の内径ｄ0 を大きくしたり、開口部の幅δ0 を狭くしても、止め輪外れを防止できる。しかし、これらの寸法を変えた場合は、軸受組立時に止め輪を従来より大きく変形させることが必要となり、作業性が悪化する。従って、（１）式を成立させるには、断面高さＨを従来よりも大きくすることが好ましい。
【００１９】
【発明の効果】
以上のように、この発明の複列転がり軸受は、軸への組込作業中に、２個の内輪を締結する止め輪が縮径しても両内輪の環状溝から外れる部分が生じないように、止め輪の断面高さを設定したものであるから、従来と同等の作業性を確保しつつ、止め輪外れを防止して、組込作業の能率を向上させることができる。
【図面の簡単な説明】
【図１】実施形態の複列転がり軸受の縦断面図
【図２】ａ、ｂは、それぞれ図１の軸受の止め輪の正面図および縦断面図
【図３】図１の軸受の止め輪が縮径した状態での位置および寸法関係を示す説明図
【符号の説明】
１ 外輪
１ａ、１ｂ 軌道面
２ 内輪
２ａ 軌道面
２ｂ 凹部
３ 内輪
３ａ 軌道面
３ｂ 凹部
４ ころ
５ 保持器
６ 止め輪
７ 環状溝
Ａ 軸[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a double-row rolling bearing in which two inner rings are fastened with a retaining ring.
[0002]
[Prior art]
Some double-row rolling bearings in which rolling elements are incorporated in two rows between inner and outer rings have two inner rings each having one row of raceway surfaces fastened by abutting end faces.
[0003]
As shown in FIG. 1, which is an embodiment of the present invention, an inner ring fastening structure of this type of double row rolling bearing includes concave portions 2b, 3b having an L-shaped cross section on the inner diameter surface near the abutting end of each inner ring 2, 3. An annular groove 7 is provided so that the concave portions 2b and 3b are opposed to each other so that a retaining ring 6 having a concave cross section is fitted into an annular groove 7 having a concave cross section formed over both inner rings 2 and 3. There are many things. The retaining ring 6 is a C-shape having an opening formed at one location in the circumferential direction, and is fitted in the annular groove 7 with the opening narrowed. 2, 3 are integrated (for example, refer to Patent Documents 1 and 2).
[0004]
[Patent Document 1]
JP 2001-289255 A [Patent Document 2]
Published Japanese Utility Model Application No. Hei 3-20725
[Problems to be solved by the invention]
When assembling the double row rolling bearing of the inner ring fastening structure described above to the shaft, when the outer end of one of the two inner rings fastened by the retaining ring is fitted to the shaft end, the inner ring and Due to the gap between the shafts, the axes of the two inner rings are slightly inclined, and it is often necessary to push the inner rings into the shaft while swinging them in the circumferential direction.
[0006]
At this time, depending on the surface properties of the shaft and the inclination of the inner ring with respect to the shaft, the frictional force between the shaft and one of the inner rings becomes larger than the frictional force between the two inner rings, and the relative circumferential position between the two inner rings. Shift occurs. If the positions of the inner rings in the circumferential direction are shifted, the retaining ring receives a shear force in the circumferential direction and is reduced in diameter, so that a part of the ring in the circumferential direction is disengaged from the annular groove. When it is received, the whole may come off from the annular groove. When the retaining ring comes off, the inner ring which has been pushed halfway must be pulled back and the retaining ring must be refitted, which greatly reduces the efficiency of the assembling work.
[0007]
On the other hand, by increasing the sectional modulus of the retaining ring and increasing the elastic restoring force in the radially enlarged direction in a state of being fitted in the annular groove, relative displacement between the inner rings in the circumferential direction is less likely to occur. be able to. However, when this method is adopted, a large diameter reducing force is required when the retaining ring is mounted on the inner peripheral side of the inner ring, and the workability is greatly deteriorated.
[0008]
Therefore, an object of the present invention is to prevent detachment of a retaining ring while securing workability in a work of assembling a double row rolling bearing in which two inner rings are fastened by retaining rings.
[0009]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the present invention defines the cross-sectional height of the retaining ring so that even if the retaining ring is reduced in diameter until its opening is closed, a portion does not come off from the annular grooves of both inner rings. is there. As a result, even if both inner rings are pushed into the shaft while the retaining ring is the most reduced in diameter, the retaining ring is pushed and expanded on the shaft, and the whole is fitted into the annular groove, causing the retaining ring to come off. It can be difficult.
[0010]
Specifically, the two inner races are butted against each other at their end faces, and an L-shaped cross-section recess provided annularly on the inner diameter surface near the abutting end of the two inner races is opposed to each other, so that the annular shape of the concave cross-section straddles both the inner races. A double-row rolling bearing in which both inner rings are integrally fastened by forming a groove and fitting a retaining ring having a concave cross section and an opening at one location in the circumferential direction into the annular groove, the cross section of the retaining ring The height H is set based on the inner diameter d of the inner ring, the inner diameter d 0 of the retaining ring, and the width δ 0 of the opening so that the following equation (1) is satisfied.
[0011]
H> d−d 0 + δ 0 / π (1)
In the above equation (1), the retaining ring in a state where the diameter is reduced until the opening is closed (inner diameter: d 0 −δ 0 / π) is deviated from the axis of the inner ring, and is completely annular at a certain position in the circumferential direction. This is derived from the condition that at least the outer peripheral edge portion enters the annular groove at a position on the opposite side in the circumferential direction when the inner ring is fitted inside (the inner ring surface of the retaining ring and the inner ring coincide with each other).
[0012]
BEST MODE FOR CARRYING OUT THE INVENTION
An embodiment of the present invention will be described below with reference to FIGS. FIG. 1 shows a state in which the double-row rolling bearing is being assembled on the shaft A. The bearing has an outer race 1 having two rows of raceways 1a and 1b, two inner races 2 and 3 having raceways 2a and 3a facing the respective raceways 1a and 1b of the outer race 1, and opposing each other. It basically comprises two rows of tapered rollers 4 rolling between the raceway surfaces 1a, 2a and 1b, 3a, and retainers 5 holding the tapered rollers 4 in each row. The two inner rings 2 and 3 are integrally fastened by a retaining ring 6 mounted on the inner peripheral side thereof in a state where the inner rings 2 and 3 are abutted on each other.
[0013]
As described above, the fastening structure of the inner races 2 and 3 butted with each other at the end surfaces is provided with concave portions 2 b and 3 b having an L-shaped cross section on the inner diameter surface near the butted ends of the respective inner races 2 and 3. The concave grooves 2b, 3b are opposed to each other to form an annular groove 7 having a concave cross section that straddles both inner rings 2, 3, and a snap ring 6 having a concave cross section is fitted into the annular groove 7. As shown by a solid line in FIG. 2 (a), the retaining ring 6 is a C-shape having an opening formed at one location in the circumferential direction, and is fitted in the annular groove 7 with the opening being narrowed. The two inner rings 2 and 3 are integrated by the elastic restoring force in the diameter expanding direction.
[0014]
As shown in FIGS. 2 (a) and 2 (b), the dimensions of the retaining ring 6 are as follows: the inner diameter is d 0 , the width of the opening is δ 0 , the sectional height is H, and the inner diameter of the inner rings 2 and 3 is When d is set, the following equation (1) is established. In this embodiment, as shown in FIG. 1, a tapered portion for smoothly fitting the retaining ring 6 into the annular groove 7 at the time of assembling the bearing is provided at the edges of the annular grooves 7 of the inner rings 2 and 3. The diameter of the inner peripheral cylindrical surface of each of the inner rings 2 and 3 is added to the depth of the tapered portion to form an inner ring inner diameter d for setting the size of the retaining ring.
[0015]
H> d−d 0 + δ 0 / π (1)
This bearing has the above configuration, and as shown in FIG. 1, the outer end of one of the inner rings 3 is fitted to the end of the shaft A, and the inner rings 2 and 3 are incorporated into the shaft A while swinging in the circumferential direction. As a result, the retaining ring 6 receives a circumferential shearing force due to the relative displacement of the inner rings 2 and 3 in the circumferential direction, and as shown by a dotted line in FIG. There is a possibility that the diameter is reduced until it closes (the inner diameter becomes d 0 −δ 0 / π).
[0016]
However, as shown in FIG. 3, the retaining ring 6, whose diameter is reduced until the opening is closed, completely fits into the annular groove 7 at a position in the circumferential direction shifted from the axis of the inner rings 2, 3. Even in the case where the retaining ring 6 and the inner rings 2 and 3 have the same inner diameter surface, the retaining ring 6 has a sectional height H that satisfies the above expression (1), and therefore at least is located at a position on the opposite side in the circumferential direction. The outer peripheral edge enters the annular groove 7. If the inner rings 2 and 3 are pushed into the shaft A in this state, the retaining ring 6 is pushed and expanded by the shaft A, and the whole is fitted into the annular groove 7.
[0017]
That is, in this bearing, even if the retaining ring receives a shear force in the circumferential direction and is reduced in diameter during the assembling work on the shaft, the retaining ring does not come off the annular groove at any position in the circumferential direction. Detachment can be prevented. At the time of assembling the bearing, by deforming the retaining ring into a coil spring shape, the retaining ring can be mounted on the inner peripheral side of the inner ring without any inconvenience.
[0018]
In the above equation (1), the dimensions of the retaining ring are defined so that even if the retaining ring mounted on the bearing is reduced in diameter until its opening is closed, a portion does not come off from the annular groove. Even if the inner diameter d 0 of the retaining ring is increased or the width δ 0 of the opening is reduced so as to satisfy the expression (3), the retaining ring can be prevented from coming off. However, when these dimensions are changed, it is necessary to deform the retaining ring to a greater extent than before in assembling the bearing, thereby deteriorating workability. Therefore, in order to satisfy the expression (1), it is preferable to make the sectional height H larger than before.
[0019]
【The invention's effect】
As described above, the double-row rolling bearing of the present invention is configured such that, during the assembling work on the shaft, even if the retaining ring that fastens the two inner rings is reduced in diameter, a portion that does not come off from the annular groove of both inner rings is generated. In addition, since the cross-section height of the retaining ring is set, it is possible to prevent the retaining ring from coming off and improve the efficiency of the assembling work while securing the same operability as before.
[Brief description of the drawings]
1 is a longitudinal sectional view of a double-row rolling bearing according to an embodiment; FIG. 2 is a front view and a longitudinal sectional view of a retaining ring of the bearing of FIG. 1; FIG. Explanatory drawing showing the position and dimensional relationship in the state where the diameter is reduced [Description of reference numerals]
REFERENCE SIGNS LIST 1 outer ring 1a, 1b raceway surface 2 inner ring 2a raceway surface 2b recess 3 inner ring 3a raceway surface 3b recess 4 roller 5 retainer 6 retaining ring 7 annular groove A shaft

Claims (2)

２個の内輪を端面どうしで突き合わせ、両内輪の突き合わせ端近傍の内径面に環状に設けたＬ字形断面の凹部を対向させて、両内輪に跨がる凹形断面の環状溝を形成し、この環状溝に断面が凹形で周方向の一箇所に開口部を有する止め輪を嵌め込むことにより、両内輪を一体に締結した複列転がり軸受において、前記止め輪がその開口部が閉じるまで縮径しても前記両内輪の環状溝から外れる部分が生じないように、止め輪の断面高さを規定したことを特徴とする複列転がり軸受。The two inner rings are butted against each other at their end faces, and an L-shaped cross-section concave portion provided annularly is opposed to the inner diameter surface near the butting end of both inner rings to form an annular groove having a concave cross-section straddling both inner rings, In a double row rolling bearing in which both inner rings are integrally fastened by fitting a retaining ring having a concave cross section and an opening at one location in the circumferential direction into this annular groove, the retaining ring is closed until the opening is closed. A double row rolling bearing wherein the cross-section height of the retaining ring is defined so that even if the diameter is reduced, a portion of the inner ring does not deviate from the annular groove. 前記止め輪の断面高さＨを、前記内輪の内径ｄと、止め輪の内径ｄ0 および開口部の幅δ0 とに基づいて、下記（１）式が成立するように設定したことを特徴とする複列転がり軸受。
Ｈ＞ｄ−ｄ0 ＋δ0 ／π ・・・ （１）The sectional height H of the retaining ring is set based on the inner diameter d of the inner ring, the inner diameter d 0 of the retaining ring, and the width δ 0 of the opening so that the following equation (1) is satisfied. And double row rolling bearing.
H> d−d 0 + δ 0 / π (1)
JP2002364939A 2002-12-17 2002-12-17 Double row rolling bearing Expired - Fee Related JP4262974B2 (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013104446A (en) * 2011-11-10 2013-05-30 Nsk Ltd Multi-row rolling bearing
JP2015132351A (en) * 2014-01-15 2015-07-23 株式会社ジェイテクト Double row rolling bearing
US20160201725A1 (en) * 2013-10-14 2016-07-14 Schaeffler Technologies AG & Co. KG Pre-mounting of a gap-optimized clip ring between inner rings of an anti-friction bearing
DE102015218996A1 (en) * 2015-10-01 2017-04-06 Aktiebolaget Skf Connecting means and method for mounting a connecting means for sealingly connecting a first and a second bearing ring together

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013104446A (en) * 2011-11-10 2013-05-30 Nsk Ltd Multi-row rolling bearing
US20160201725A1 (en) * 2013-10-14 2016-07-14 Schaeffler Technologies AG & Co. KG Pre-mounting of a gap-optimized clip ring between inner rings of an anti-friction bearing
US9677619B2 (en) * 2013-10-14 2017-06-13 Schaeffler Technologies AG & Co. KG Pre-mounting of a gap-optimized clip ring between inner rings of an anti-friction bearing
JP2015132351A (en) * 2014-01-15 2015-07-23 株式会社ジェイテクト Double row rolling bearing
DE102015218996A1 (en) * 2015-10-01 2017-04-06 Aktiebolaget Skf Connecting means and method for mounting a connecting means for sealingly connecting a first and a second bearing ring together
DE102015218996B4 (en) 2015-10-01 2019-04-18 Aktiebolaget Skf Connecting means for sealingly connecting a first and a second bearing ring together

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