JP2003074547A - Matched ball bearing unit - Google Patents
Matched ball bearing unitInfo
- Publication number
- JP2003074547A JP2003074547A JP2001260818A JP2001260818A JP2003074547A JP 2003074547 A JP2003074547 A JP 2003074547A JP 2001260818 A JP2001260818 A JP 2001260818A JP 2001260818 A JP2001260818 A JP 2001260818A JP 2003074547 A JP2003074547 A JP 2003074547A
- Authority
- JP
- Japan
- Prior art keywords
- outer ring
- ball bearing
- bearing unit
- ball bearings
- axial direction
- 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.)
- Pending
Links
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明に係る組み合わせ玉
軸受ユニットは、例えば自動車用補機の回転軸をハウジ
ングに対し回転自在に支持する為に使用する。特に、本
発明の組み合わせ玉軸受ユニットは、ハイブリッド車用
の発電機を兼ねた電動モータ、或はアイドリングストッ
プ車用のスタータモータの様に、高荷重、高回転と言っ
た厳しい使用条件の下で使用される用途でも優れた耐久
性を得られる構造を実現するものである。BACKGROUND OF THE INVENTION The combined ball bearing unit according to the present invention is used, for example, to rotatably support a rotary shaft of an automobile accessory with respect to a housing. In particular, the combined ball bearing unit of the present invention is used under severe conditions such as high load and high rotation like an electric motor that also functions as a generator for hybrid vehicles or a starter motor for idling stop vehicles. It realizes a structure that can obtain excellent durability even in the intended use.
【０００２】[0002]
【従来の技術】例えば、走行用の駆動源としてエンジン
と電動モータとを使い分けるハイブリッド車の場合、こ
れらエンジンのクランクシャフトの端部に設けたプーリ
と、電動モータの回転軸に設けたプーリとを、無端ベル
トを介して接続する構造が一部で提案されている。この
様な構造の場合、上記電動モータの回転軸を支持する為
の転がり軸受は、高荷重の下で高速回転する。この様な
厳しい使用条件を満たす為に従来は、単列深溝型の玉軸
受か、或は図２に示す様な組み合わせ玉軸受ユニット１
を使用する事が考えられていた。2. Description of the Related Art For example, in the case of a hybrid vehicle in which an engine and an electric motor are selectively used as driving sources for traveling, a pulley provided at an end of a crankshaft of the engine and a pulley provided on a rotary shaft of the electric motor are provided. In some cases, a structure for connecting via an endless belt has been proposed. In such a structure, the rolling bearing for supporting the rotating shaft of the electric motor rotates at high speed under a high load. In order to satisfy such severe use conditions, conventionally, a single row deep groove type ball bearing or a combined ball bearing unit 1 as shown in FIG. 2 is used.
Was considered to be used.
【０００３】この組み合わせ玉軸受ユニット１は、それ
ぞれが単列深溝型である１対の玉軸受２、２を、軸方向
に重ね合わせる事により構成している。これら各玉軸受
２、２はそれぞれ、外周面に深溝型の内輪軌道３を有す
る内輪４と、内周面に外輪軌道５を有する外輪６と、こ
れら内輪軌道３と外輪軌道５との間に転動自在に設けら
れた複数個の玉７とを備える。これら各玉７は、保持器
８により転動自在に保持している。それぞれがこの様な
構成を有する、上記各玉軸受２、２は、それぞれの内輪
４、４の軸方向一端面同士、外輪６、６の軸方向一端面
同士を突き合わせた状態で、互いに同心に組み合わせ
る。又、これら各外輪６、６の軸方向他端部内周面にそ
れぞれの外周縁部を係止したシールリング９、９の内周
縁部に形成したシールリップの先端縁を、上記各内輪
４、４の軸方向他端部表面に、全周に亙って摺接させて
いる。そして、上記１対のシールリング９、９により、
上記各玉７、７を設置した空間１０内に封入したグリー
スが外部に漏洩する事を防止すると共に、外部に存在す
る塵芥等の異物が上記空間１０内に入り込む事を防止し
ている。This combination ball bearing unit 1 is constructed by stacking a pair of ball bearings 2, 2 each of which is a single row deep groove type in the axial direction. Each of these ball bearings 2, 2 has an inner ring 4 having a deep groove type inner ring raceway 3 on its outer peripheral surface, an outer ring 6 having an outer ring raceway 5 on its inner peripheral surface, and between these inner ring raceway 3 and outer ring raceway 5. And a plurality of balls 7 provided so as to be freely rollable. Each of these balls 7 is held by a retainer 8 so as to be rollable. The ball bearings 2, 2 each having such a configuration are concentric with each other in a state in which the axial one end faces of the inner rings 4, 4 and the axial one end faces of the outer rings 6, 6 are butted against each other. combine. Further, the tip edges of the seal lips formed on the inner peripheral edge portions of the seal rings 9, 9 having the outer peripheral edge portions locked to the inner peripheral surfaces of the other axial end portions of the outer ring portions 6, 6 are provided with the inner ring portions 4, It is in sliding contact with the surface of the other end of the shaft 4 in the axial direction over the entire circumference. Then, by the pair of seal rings 9 and 9,
The grease enclosed in the space 10 in which the balls 7, 7 are installed is prevented from leaking to the outside, and foreign matter such as dust existing outside is prevented from entering the space 10.
【０００４】[0004]
【発明が解決しようとする課題】図２に示す様な従来か
ら考えられていた構造の場合には、次の〜の点で、
改良が望まれている。
各玉軸受２、２に組み込める玉７、７の数が少ない
為、小型でしかも負荷容量の大きな構造を実現する事が
難しい。
ミスアライメントに対する許容量が少ない為、組み
付け作業に高精度が要求される。
軸方向寸法の短縮を図る事に就いて、特に考慮され
てはいない。In the case of the conventionally conceived structure as shown in FIG. 2, the following points
Improvement is desired. Since the number of balls 7, 7 that can be incorporated in each ball bearing 2, 2 is small, it is difficult to realize a compact structure with a large load capacity. Since there is little tolerance for misalignment, high precision is required for assembly work. No particular consideration has been given to reducing the axial dimension.
【０００５】これら〜の様な問題が生じる理由は、
次の通りである。このうちのの問題は、上記各玉軸受
２、２に設けた内輪軌道３及び外輪軌道５が、何れも深
溝型である事により生じる。即ち、それぞれが深溝型で
ある内輪軌道３と外輪軌道５との間に玉７を組み込む場
合には、内輪４と外輪６とを互いに偏心させ、この内輪
４の端部外周面と外輪６の端部内周面との間の隙間を、
円周方向の一部で大きくする。そして、この様に大きく
した隙間部分を通じて、上記内輪軌道３と上記外輪軌道
５との間に複数個の玉７を組み込んだ後、これら各玉７
を円周方向に関し等間隔に分散させる。従って、上記内
輪軌道３と上記外輪軌道５との間に組み込める玉７の数
が限られ、上記各玉軸受２、２の負荷容量を大きくする
事が難しい。The reason why these problems (1) to (3) occur is as follows.
It is as follows. The problem among them occurs because the inner ring raceway 3 and the outer ring raceway 5 provided on each of the ball bearings 2 and 2 are deep groove type. That is, when the balls 7 are installed between the inner ring raceway 3 and the outer ring raceway 5, each of which is a deep groove type, the inner ring 4 and the outer ring 6 are eccentric to each other, and the end outer peripheral surface of the inner ring 4 and the outer ring 6 are separated from each other. The gap between the inner surface of the end,
Increase in part in the circumferential direction. Then, after incorporating a plurality of balls 7 between the inner ring raceway 3 and the outer ring raceway 5 through the gaps thus enlarged, each of these balls 7
Are evenly distributed in the circumferential direction. Therefore, the number of balls 7 that can be incorporated between the inner ring raceway 3 and the outer ring raceway 5 is limited, and it is difficult to increase the load capacity of each of the ball bearings 2 and 2.
【０００６】次に、上記の問題は、それぞれが深溝型
である１対の玉軸受２、２を組み合わせて成る組み合わ
せ玉軸受ユニット１のモーメント剛性が高い事に基づ
く。即ち、互いに内輪４及び外輪６の端面同士を突き合
わせて上記組み合わせ玉軸受ユニット１を構成した上記
各玉軸受２、２の接触角は、これら各玉軸受２、２に関
する作用線の方向を表す為に図２に記載した鎖線α、α
から明らかな通り、０度となる。周知の様に、組み合わ
せ玉軸受ユニットのモーメント剛性は、作用線の方向を
表す１対の直線α、αと中心線ｘとの交点同士の距離Ｌ
0 が長い程高くなる。そして、モーメント剛性が高い
程、ミスアライメントが生じた場合に、上記各玉７、７
の転動面と上記各内輪軌道３、３及び外輪軌道５、５と
の当接部に過大な面圧が加わり易くなる。言い換えれ
ば、モーメント剛性が高い程、ミスアライメントに対す
る許容量が小さくなる。Next, the above problem is based on the fact that the combined ball bearing unit 1, which is a combination of a pair of deep groove type ball bearings 2 and 2, has a high moment rigidity. That is, the contact angle of each of the ball bearings 2 and 2 constituting the combined ball bearing unit 1 by abutting the end faces of the inner ring 4 and the outer ring 6 against each other represents the direction of the line of action for each of the ball bearings 2 and 2. The chain lines α and α shown in FIG.
As is clear from, it becomes 0 degree. As is well known, the moment rigidity of the combined ball bearing unit is a distance L between the intersections of a pair of straight lines α, α representing the direction of the action line and the center line x.
The higher the value of 0, the higher the value. The higher the moment rigidity is, the more misalignment occurs and the balls 7, 7
An excessive surface pressure is likely to be applied to the abutting portions of the rolling surfaces of the inner ring raceways 3 and 3 and the outer ring raceways 5 and 5. In other words, the higher the moment stiffness, the smaller the tolerance for misalignment.
【０００７】図２に示した構造の場合、上記距離Ｌ0 が
大きい為、上記各内輪軌道３、３の中心軸と上記各外輪
軌道５、５の中心軸との傾きを極く小さく納める必要が
ある等、組み付け作業が面倒になる。上記組み合わせ玉
軸受ユニット１により支持する回転軸は、この組み合わ
せ玉軸受ユニット１から軸方向に離れた部分に設けた別
の転がり軸受によっても支持する為、上記回転軸に加わ
るモーメント荷重は、上記組み合わせ玉軸受ユニット１
と上記別の転がり軸受との両方により支承する。従っ
て、この複列玉軸受１単独でのモーメント剛性は高い必
要はなく、ミスアライメントに対する許容量を大きくす
る面からは、むしろ小さい方が好ましい。In the case of the structure shown in FIG. 2, since the distance L 0 is large, the inclination between the central axes of the inner ring raceways 3 and 3 and the central axes of the outer ring raceways 5 and 5 must be set to be extremely small. As a result, assembly work becomes troublesome. Since the rotary shaft supported by the combined ball bearing unit 1 is also supported by another rolling bearing provided in a portion axially distant from the combined ball bearing unit 1, the moment load applied to the rotary shaft is the same as the combination described above. Ball bearing unit 1
And the other rolling bearing described above. Therefore, the moment rigidity of the double-row ball bearing 1 alone does not need to be high, and it is rather smaller from the viewpoint of increasing the tolerance for misalignment.
【０００８】更に、前記の問題は、単なる単列深溝型
の玉軸受を構成する為の内輪４及び外輪６をそのまま使
用している事に基づく。即ち、上記組み合わせ玉軸受ユ
ニット１を構成する為に、１対の玉軸受２、２の内輪
４、４及び外輪６、６の端面同士を突き合わせている
為、突き合わせ面側のシールリングは不要になる。この
為、突き合わせ面と反対側にのみシールリング９、９を
装着しているが、上記各内輪４、４及び外輪６、６とし
ては、上記突き合わせ面側にもシールリングを装着可能
な、軸方向に関して対称な形状のものをそのまま使用し
ている。この為、上記突き合わせ面側にも、シールリン
グを装着する為の係止溝が存在し、その分、軸方向寸法
が嵩んでしまう。軸方向寸法を大きくする事は、上記組
み合わせ玉軸受ユニット１自体のモーメント剛性を高く
する事には効果があるが、本発明の対象となる様な組み
合わせ玉軸受ユニットの場合、この組み合わせ玉軸受ユ
ニット自体のモーメント剛性が高くなる事がむしろ有害
である事は、上述した通りである。本発明は、この様な
事情に鑑みて、小型でしかも負荷容量が大きく、且つ、
ミスアライメントに対する許容量が多く、しかも、軸方
向寸法の短縮を図れる組み合わせ玉軸受ユニットを実現
すべく発明したものである。Further, the above problem is based on the fact that the inner ring 4 and the outer ring 6 for forming a simple single-row deep groove type ball bearing are used as they are. That is, since the end faces of the inner rings 4 and 4 and the outer rings 6 and 6 of the pair of ball bearings 2 and 2 are butted to each other in order to configure the above-mentioned combined ball bearing unit 1, a seal ring on the butted face side is unnecessary. Become. For this reason, the seal rings 9 and 9 are mounted only on the side opposite to the abutting surface, but as the inner rings 4 and 4 and the outer rings 6 and 6, the seal rings can be mounted also on the abutting surface side. The one that is symmetrical about the direction is used as it is. For this reason, there is a locking groove for mounting the seal ring also on the abutting surface side, and the axial dimension increases correspondingly. Increasing the axial dimension is effective in increasing the moment rigidity of the combined ball bearing unit 1 itself, but in the case of the combined ball bearing unit that is the subject of the present invention, this combined ball bearing unit As described above, increasing the moment rigidity of itself is rather harmful. In view of such circumstances, the present invention has a small size, a large load capacity, and
The invention was made in order to realize a combined ball bearing unit which has a large amount of tolerance for misalignment and which can reduce the axial dimension.
【０００９】[0009]
【課題を解決するための手段】本発明の組み合わせ玉軸
受ユニットは、前述の図２に示した様な従来から考えら
れている組み合わせ玉軸受ユニットと同様に、外周面に
内輪軌道を有する内輪と、内周面に外輪軌道を有する外
輪と、これら内輪軌道と外輪軌道との間に転動自在に設
けられた複数個の玉とを備えた単列玉軸受を１対、互い
に同心に配置した状態で、軸方向に重ね合わせて成る。
特に、本発明の組み合わせ玉軸受ユニットに於いては、
上記各外輪は、外輪軌道に対して軸方向片側の内径が軸
方向他側の内径よりも大きくなっているカウンタボア型
である。そして、それぞれがアンギュラ型である上記１
対の単列玉軸受は、それぞれの外輪の軸方向片側同士を
突き合わせて内向の接触角を付与する正面組み合わせ
（ＤＦ）で組み合わされている。更に、上記１対の単列
玉軸受のうち、互いに突き合わされる側の端部にはシー
ルリングを設けず、反対側の端部に、それぞれの内輪の
外周面と外輪の内周面との間を塞ぐシールリングを設け
ている。The combined ball bearing unit of the present invention has an inner ring having an inner ring raceway on its outer peripheral surface, as in the conventional combined ball bearing unit as shown in FIG. , A pair of single-row ball bearings having an outer ring having an outer ring raceway on the inner peripheral surface and a plurality of balls rotatably provided between the inner ring raceway and the outer ring raceway are arranged concentrically with each other. In the state, they are superposed in the axial direction.
Particularly, in the combined ball bearing unit of the present invention,
Each of the outer rings is a counterbore type in which the inner diameter on one side in the axial direction with respect to the outer ring raceway is larger than the inner diameter on the other side in the axial direction. And each of the above 1 which is an angular type
The pair of single-row ball bearings are combined in a frontal combination (DF) in which one side of each outer ring in the axial direction is butted against each other to provide an inward contact angle. Further, of the pair of single-row ball bearings, no seal ring is provided at the ends that are abutted with each other, and the opposite ends have the outer peripheral surface of each inner ring and the inner peripheral surface of the outer ring. A seal ring is provided to close the gap.
【００１０】[0010]
【作用】上述の様に構成する本発明によれば、小型で
（大径化する事なく）しかも負荷容量が大きくて高荷重
下での使用も可能で、且つ、ミスアライメントに対する
許容量が多く、しかも、軸方向寸法の短縮を図れる組み
合わせ玉軸受ユニットを実現できる。According to the present invention configured as described above, it is small (without increasing the diameter), has a large load capacity, can be used under a high load, and has a large allowance for misalignment. Moreover, it is possible to realize a combined ball bearing unit that can reduce the axial dimension.
【００１１】[0011]
【発明の実施の形態】図１は、本発明の実施の形態の１
例を示している。本発明の組み合わせ玉軸受ユニット１
ａは、それぞれがアンギュラ型である１対の玉軸受２
ａ、２ａを、互いに同心に、軸方向に重ね合わせる事に
より構成している。これら各玉軸受２ａ、２ａはそれぞ
れ、外周面に深溝型の内輪軌道３を有する内輪４と、内
周面にアンギュラ型の外輪軌道５ａを有する外輪６ａ
と、これら内輪軌道３と外輪軌道５ａとの間に転動自在
に設けられた複数個の玉７とを備える。特に、本発明の
組み合わせ玉軸受ユニット１ａを構成する上記各玉軸受
２ａ、２ａを構成する外輪６ａ、６ａは、上記外輪軌道
５ａに対して軸方向片側の内径が軸方向他側の内径より
も大きくなっているカウンタボア型である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a first embodiment of the present invention.
An example is shown. Combined ball bearing unit 1 of the present invention
a is a pair of angular contact ball bearings 2
a and 2a are concentrically arranged and axially overlapped with each other. Each of these ball bearings 2a, 2a has an inner ring 4 having a deep groove type inner ring raceway 3 on its outer peripheral surface and an outer ring 6a having an angular outer ring raceway 5a on its inner peripheral surface.
And a plurality of balls 7 rotatably provided between the inner ring raceway 3 and the outer ring raceway 5a. In particular, the outer rings 6a, 6a forming the respective ball bearings 2a, 2a constituting the combined ball bearing unit 1a of the present invention have an inner diameter on one side in the axial direction with respect to the inner ring on the other side in the axial direction with respect to the outer ring raceway 5a. It is a large counterbore type.
【００１２】即ち、上記各外輪６ａ、６ａは、上記外輪
軌道５ａを軸方向に関して両側から挟む部分のうち、上
記軸方向他側部分にのみ、内径が小さくなった肩部１１
を形成している。これに対して上記軸方向片側部分は、
上記外輪軌道５ａの外接円よりも僅かに内径が小さくな
った部分１２から軸方向端面に向けて内径が漸次大きく
なる、外開き状のテーパ面としている。尚、上記僅かに
内径が小さくなった部分１２は、それぞれが単列アンギ
ュラ型である上記各玉軸受２ａ、２ａをそれぞれ単独で
取り扱う場合に、上記各玉７と上記外輪６ａとが不用意
に分離しない様にする為に設ける。上記組み合わせ玉軸
受ユニット１ａとして所定の回転支持部に組み付けた状
態では不要である。従って、抑え治具等の他の手段で上
記各玉７と上記外輪６ａとが不用意に分離しない様にで
きるのであれば、上記僅かに内径が小さくなった部分１
２を省略する事もできる。この場合には、上記各外輪６
ａ、６ａの軸方向片側部分の内周面全体が、上記外輪軌
道５ａの最も内径が大きくなった部分から軸方向端面に
向けて漸次内径が大きくなる、テーパ面となる。又、上
記各玉７は、保持器８ａにより転動自在に保持してい
る。図示の例の場合、この保持器８ａとして、合成樹脂
製でもみ抜き型保持器としている。この様なもみ抜き型
の保持器８ａを使用する事により、この保持器８ａの剛
性を高めて、高速回転での使用を可能にしている。但
し、本発明を実施する場合に、前述の図２に示した様な
金属製の波形保持器を使用する事もできる。更には、使
用回転速度が低く、保持器の剛性をあまり高くする必要
がない場合には、合成樹脂製の冠型保持器とする事もで
きる。That is, each of the outer rings 6a, 6a has a shoulder portion 11 having a reduced inner diameter only at the other side in the axial direction among the portions sandwiching the outer ring raceway 5a from both sides in the axial direction.
Is formed. On the other hand, the one side portion in the axial direction is
The taper surface has an outward opening shape in which the inner diameter gradually increases from the portion 12 having the inner diameter slightly smaller than the circumscribed circle of the outer ring raceway 5a toward the axial end surface. In the case where the ball bearings 2a and 2a each having a single-row angular type are individually handled, the portion 12 having a slightly smaller inner diameter causes the balls 7 and the outer ring 6a to be careless. It is provided to prevent separation. It is unnecessary when the combined ball bearing unit 1a is assembled to a predetermined rotation support portion. Therefore, if it is possible to prevent the balls 7 and the outer ring 6a from being inadvertently separated by other means such as a holding jig, the portion 1 having a slightly smaller inner diameter is used.
2 can be omitted. In this case, each outer ring 6
The entire inner peripheral surface of the axially one side portion of a and 6a is a tapered surface in which the inner diameter gradually increases from the portion of the outer ring raceway 5a having the largest inner diameter toward the axial end surface. The balls 7 are held by a cage 8a so that they can roll. In the case of the illustrated example, the cage 8a is made of a synthetic resin and is a machined die cage. By using such a machined-type cage 8a, the rigidity of the cage 8a is increased, and the cage 8a can be used at high speed rotation. However, when carrying out the present invention, it is also possible to use a corrugated holder made of metal as shown in FIG. Further, when the rotation speed used is low and it is not necessary to increase the rigidity of the cage so much, a crown type cage made of synthetic resin can be used.
【００１３】それぞれが上述の様な構成を有する、上記
各玉軸受２ａ、２ａは、それぞれの内輪４、４の軸方向
一端面同士、外輪６ａ、６ａの軸方向一端面同士を突き
合わせた状態で組み合わせる。従って、それぞれがアン
ギュラ型である上記１対の玉軸受２ａ、２ａは、それぞ
れの外輪６ａ、６ａの軸方向片側、即ち、内径が大きく
なっている側同士を突き合わせる事により、内向の接触
角を付与する正面組み合わせで組み合わされる。又、上
記各外輪６ａ、６ａの軸方向他端部内周面にそれぞれの
外周縁部を係止したシールリング９、９の内周縁部に形
成したシールリップの先端縁を、上記各内輪４、４の軸
方向他端部表面に全周に亙って摺接させている。そし
て、上記１対のシールリング９、９により、上記各玉
７、７を設置した空間１０ａ内に封入したグリースが外
部に漏洩する事を防止すると共に、外部に存在する塵芥
等の異物が上記空間１０ａ内に入り込む事を防止してい
る。上記各玉軸受２ａ、２ａの両端部のうち、互いに突
き合わされる側には、シールリングは設けない。The ball bearings 2a, 2a each having the above-mentioned structure are arranged such that the axially one end faces of the inner rings 4, 4 are abutted with each other and the axially one end faces of the outer rings 6a, 6a are abutted with each other. combine. Therefore, the pair of ball bearings 2a and 2a, which are each of the angular type, have an inward contact angle by abutting one side of the outer rings 6a, 6a in the axial direction, that is, the side with the larger inner diameter. Are combined in a frontal combination that gives. Further, the tip ends of the seal lips formed on the inner peripheral edge portions of the seal rings 9, 9 having the outer peripheral edge portions locked to the inner peripheral surfaces of the other axial end portions of the outer ring portions 6a, 6a are provided with the inner ring portions 4, It is slidably in contact with the surface of the other end of the shaft 4 in the axial direction over the entire circumference. The pair of seal rings 9, 9 prevent the grease enclosed in the space 10a in which the balls 7, 7 are installed from leaking to the outside and prevent foreign matter such as dust existing outside from being leaked to the outside. This prevents entry into the space 10a. No seal rings are provided on the ends of each of the ball bearings 2a, 2a that are abutted against each other.
【００１４】上述の様に構成する本例によれば、小型で
しかも負荷容量が大きく、且つ、ミスアライメントに対
する許容量が多く、しかも、軸方向寸法の短縮を図れる
組み合わせ玉軸受ユニットを実現できる。先ず、小型で
しかも負荷容量が大きな構造の実現は、上記各外輪６
ａ、６ａをカウンタボア型とする事により実現できる。
即ち、カウンタボア型の外輪６ａの場合、前記外輪軌道
５ａに隣接する軸方向片側部分のうちで最も小径となっ
た部分の内径は、この外輪軌道５ａの溝底（最も内径が
大きくなった部分）の直径と同じ（前記僅かに内径が小
さくなった部分１２を設けない場合）か、或はこの直径
よりも僅かに小さい（同じく設ける場合）だけである。
従って、上記各玉軸受２ａ、２ａを組み立てるべく、前
記内輪４の外周面の深溝型の内輪軌道３の周囲に配置し
た複数の玉７を、そのまま上記外輪軌道５ａの内径側に
押し込めるか、仮に上記内輪４と上記外輪６ａとを偏心
させるとしても、その偏心量は極く僅かで済む。従っ
て、上記外輪軌道５ａと上記内輪軌道３との間に組み込
む玉７の数を多くして、組み合わせ玉軸受ユニット１ａ
の直径を大きくする事なく（小径のまま）、負荷容量を
大きくできて、高荷重を受ける条件の下での使用も可能
になる。According to the present embodiment configured as described above, it is possible to realize a combined ball bearing unit that is small in size, has a large load capacity, has a large amount of tolerance for misalignment, and can reduce the axial dimension. First, to realize a structure that is small and has a large load capacity, the outer rings 6
It can be realized by making a and 6a into a counter bore type.
That is, in the case of the counterbore type outer ring 6a, the inner diameter of the smallest diameter portion of the axially one side portion adjacent to the outer ring raceway 5a is the groove bottom of the outer ring raceway 5a (the portion having the largest inner diameter). )) (Without the slightly smaller inner diameter portion 12) or only slightly smaller (if also provided) than this diameter.
Therefore, in order to assemble the ball bearings 2a, 2a, a plurality of balls 7 arranged around the deep groove type inner ring raceway 3 on the outer peripheral surface of the inner ring 4 can be pushed into the inner ring side of the outer ring raceway 5a as it is, or temporarily. Even if the inner ring 4 and the outer ring 6a are eccentric, the amount of eccentricity is extremely small. Therefore, by increasing the number of balls 7 incorporated between the outer ring raceway 5a and the inner ring raceway 3, the combined ball bearing unit 1a is formed.
It is possible to increase the load capacity without increasing the diameter of (without changing the diameter), and it is possible to use it under the condition of high load.
【００１５】次に、ミスアライメントに対する許容量を
多くする事は、それぞれがアンギュラ型である上記１対
の玉軸受２ａ、２ａを、内向の接触角を付与する正面組
み合わせで組み合わる事により達成される。内向の接触
角を付与する正面組み合わせの場合、この接触角を適切
に規制する事により、図１に鎖線β、βで表した、上記
各玉軸受２ａ、２ａに関する作用線の方向を表す１対の
直線と、中心線ｘとの交点同士の距離Ｌ1 を、僅少乃至
は零にできる。この為、上記１対の玉軸受２ａ、２ａを
組み合わせて成る上記組み合わせ玉軸受ユニット１ａの
モーメント剛性を低くして、上記ミスアライメントに対
する許容量を多くできる。この許容量が多くなる事は、
上記組み合わせ玉軸受ユニット１ａをハウジングの内周
面と回転軸の外周面との間に組み付ける作業の容易化に
結び付く。Next, increasing the allowable amount of misalignment is achieved by combining the pair of angular bearings 2a, 2a, each of which is an angular type, in a frontal combination which gives an inward contact angle. It In the case of a frontal combination that imparts an inward contact angle, by appropriately regulating this contact angle, a pair of action lines for each of the ball bearings 2a and 2a represented by chain lines β and β in FIG. The distance L 1 between the intersections of the straight line and the center line x can be made small or zero. Therefore, the moment rigidity of the combined ball bearing unit 1a formed by combining the pair of ball bearings 2a and 2a can be lowered, and the allowable amount for the misalignment can be increased. The increase in this allowance is
This facilitates the work of assembling the combined ball bearing unit 1a between the inner peripheral surface of the housing and the outer peripheral surface of the rotary shaft.
【００１６】更に、軸方向寸法の短縮を図る事は、上記
１対の玉軸受２ａ、２ａのうち、互いに突き合わされる
側の端部にはシールリングを設けず、反対側の端部にの
み、それぞれの内輪４の外周面と外輪６ａの内周面との
間を塞ぐシールリング９を設ける事により達成される。
上記突き合わされる側の端部にシールリングを設けない
為、この端部側で上記外輪６ａ及び内輪４の肉を除き
（互いに突き合わせる軸方向端面を、外輪軌道５ａ或は
内輪軌道３を形成した部分に近づけ）、上記１対の玉軸
受２ａ、２ａに設けた内輪軌道３、３同士及び外輪軌道
５ａ、５ａ同士を、これら両玉軸受２ａ、２ａを構成す
る玉７、７（更にはこれら各玉７、７を保持する保持器
８ａ、８ａ）同士が干渉しない程度に近づける事ができ
る。そして、この様に内輪軌道３、３及び外輪軌道５
ａ、５ａ同士を近づけた分、軸方向寸法の短縮による小
型化を図れる。Further, in order to reduce the axial dimension, a seal ring is not provided at the ends of the pair of ball bearings 2a, 2a which are in abutment with each other, but only at the opposite ends. This is achieved by providing a seal ring 9 that closes the space between the outer peripheral surface of each inner ring 4 and the inner peripheral surface of the outer ring 6a.
Since the seal ring is not provided at the end portion on the side to be abutted, the outer ring 6a and the inner ring 4 are removed from the end portion side (the axial end faces abutting each other are formed to form the outer ring raceway 5a or the inner ring raceway 3). The inner ring raceways 3, 3 provided on the pair of ball bearings 2a, 2a and the outer ring raceways 5a, 5a provided on the pair of ball bearings 2a, 2a. The cages 8a, 8a for holding the balls 7, 7 can be brought close to each other without interfering with each other. Then, in this way, the inner ring raceways 3 and 3 and the outer ring raceway 5
Since a and 5a are moved closer to each other, the size can be reduced by shortening the axial dimension.
【００１７】[0017]
【発明の効果】本発明は、以上に述べた通り構成し作用
して、小型でしかも負荷容量が大きく（高荷重化での使
用が可能で）、且つ、ミスアライメントに対する許容量
が多く、しかも、軸方向寸法の短縮を図れる組み合わせ
玉軸受ユニットを実現できる。この為、例えばハイブリ
ッド車用の発電機を兼ねた電動モータ、或はアイドリン
グストップ車用のスタータモータの様に、高荷重、高回
転と言った厳しい使用条件の下で使用される用途でも優
れた耐久性を得られる構造を、低コストで実現できる。The present invention is constructed and operated as described above, is small in size, has a large load capacity (can be used under a high load), and has a large allowance for misalignment. It is possible to realize a combined ball bearing unit that can reduce the axial dimension. For this reason, it is excellent in applications such as electric motors that also function as generators for hybrid vehicles, or starter motors for idling stop vehicles, which are used under severe operating conditions such as high load and high rotation. A structure with durability can be realized at low cost.
【図１】本発明の実施の形態の１例を示す半部断面図。FIG. 1 is a half sectional view showing an example of an embodiment of the present invention.
【図２】従来構造の１例を示す半部断面図。FIG. 2 is a half sectional view showing an example of a conventional structure.
１、１ａ 組み合わせ玉軸受ユニット ２、２ａ 玉軸受 ３ 内輪軌道 ４ 内輪 ５、５ａ 外輪軌道 ６、６ａ 外輪 ７ 玉 ８、８ａ 保持器 ９ シールリング １０、１０ａ 空間 １１ 肩部 １２ 僅かに内径が小さくなった部分 1, 1a Combination ball bearing unit 2, 2a ball bearing 3 Inner ring track 4 inner ring 5, 5a Outer ring raceway 6,6a outer ring 7 balls 8, 8a cage 9 seal ring 10, 10a space 11 Shoulder 12 Part where the inner diameter is slightly smaller
Claims (2)
面に外輪軌道を有する外輪と、これら内輪軌道と外輪軌
道との間に転動自在に設けられた複数個の玉とを備えた
単列玉軸受を１対、軸方向に重ね合わせて成る組み合わ
せ玉軸受ユニットに於いて、上記各外輪は、外輪軌道に
対して軸方向片側の内径が軸方向他側の内径よりも大き
くなっているカウンタボア型であって、それぞれがアン
ギュラ型である上記１対の単列玉軸受は、それぞれの外
輪の軸方向片側同士を突き合わせて内向の接触角を付与
する正面組み合わせで組み合わされており、上記１対の
単列玉軸受のうち、互いに突き合わされる側の端部には
シールリングを設けず、反対側の端部に、それぞれの内
輪の外周面と外輪の内周面との間を塞ぐシールリングを
設けている事を特徴とする組み合わせ玉軸受ユニット。1. An inner ring having an inner ring raceway on an outer peripheral surface, an outer ring having an outer ring raceway on an inner peripheral surface, and a plurality of balls rotatably provided between the inner ring raceway and the outer ring raceway. In a combined ball bearing unit that is formed by stacking a pair of single-row ball bearings in the axial direction, each outer ring has an inner diameter on one side in the axial direction larger than the inner diameter on the other side with respect to the outer ring raceway. The pair of single row ball bearings, which are counter bore type and angular type, are combined in a frontal combination in which one axial side of each outer ring is abutted against each other to provide an inward contact angle. Of the pair of single-row ball bearings, a seal ring is not provided at the ends that are abutted with each other, and the opposite ends are provided with an outer peripheral surface of each inner ring and an inner peripheral surface of the outer ring. Features a seal ring to close the And a combination ball bearing unit.
もみ抜き型の保持器により保持されている、請求項１に
記載した組み合わせ玉軸受ユニット。2. A plurality of balls constituting each single-row ball bearing,
The combined ball bearing unit according to claim 1, which is held by a machined cage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001260818A JP2003074547A (en) | 2001-08-30 | 2001-08-30 | Matched ball bearing unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001260818A JP2003074547A (en) | 2001-08-30 | 2001-08-30 | Matched ball bearing unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003074547A true JP2003074547A (en) | 2003-03-12 |
| JP2003074547A5 JP2003074547A5 (en) | 2008-10-16 |
Family
ID=19087960
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001260818A Pending JP2003074547A (en) | 2001-08-30 | 2001-08-30 | Matched ball bearing unit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003074547A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009520937A (en) * | 2005-12-23 | 2009-05-28 | シエフレル・コマンデイトゲゼルシヤフト | Radial rolling bearings, especially single row spherical roller bearings |
| JP2009236278A (en) * | 2008-03-28 | 2009-10-15 | Nsk Ltd | Bearing device |
| JP2011509527A (en) * | 2008-01-11 | 2011-03-24 | ケイドン コーポレイション | Pivot arm assembly for semiconductor wafer handling robot and manufacturing method thereof |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06280860A (en) * | 1993-03-02 | 1994-10-07 | Nippon Seiko Kk | Ball bearing device |
| JP2001016323A (en) * | 1999-06-28 | 2001-01-19 | Nec Saitama Ltd | On-vehicle portable telephone system and operating method of the on-vehicle portable telephone |
| JP2001163231A (en) * | 1999-09-30 | 2001-06-19 | Ntn Corp | Motor-driven power steering device |
-
2001
- 2001-08-30 JP JP2001260818A patent/JP2003074547A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06280860A (en) * | 1993-03-02 | 1994-10-07 | Nippon Seiko Kk | Ball bearing device |
| JP2001016323A (en) * | 1999-06-28 | 2001-01-19 | Nec Saitama Ltd | On-vehicle portable telephone system and operating method of the on-vehicle portable telephone |
| JP2001163231A (en) * | 1999-09-30 | 2001-06-19 | Ntn Corp | Motor-driven power steering device |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009520937A (en) * | 2005-12-23 | 2009-05-28 | シエフレル・コマンデイトゲゼルシヤフト | Radial rolling bearings, especially single row spherical roller bearings |
| JP2011509527A (en) * | 2008-01-11 | 2011-03-24 | ケイドン コーポレイション | Pivot arm assembly for semiconductor wafer handling robot and manufacturing method thereof |
| JP2009236278A (en) * | 2008-03-28 | 2009-10-15 | Nsk Ltd | Bearing device |
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