JP2003097576A - Bearing device - Google Patents
Bearing deviceInfo
- Publication number
- JP2003097576A JP2003097576A JP2001288548A JP2001288548A JP2003097576A JP 2003097576 A JP2003097576 A JP 2003097576A JP 2001288548 A JP2001288548 A JP 2001288548A JP 2001288548 A JP2001288548 A JP 2001288548A JP 2003097576 A JP2003097576 A JP 2003097576A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- housing
- rolling
- bearing device
- diameter
- 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
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、例えばＶＴＲやテ
ープストリーマ用のドラムスピンドルモータ、ＬＢＰ用
モータやＨＤＤモータ等のディスクメモリスピンドルモ
ータ、ＨＤＤのスイングアームの回転支持部やその他の
モータに組み込まれる軸受装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is incorporated in, for example, a drum spindle motor for a VTR or a tape streamer, a disk memory spindle motor such as an LBP motor or an HDD motor, a rotation support portion of a swing arm of an HDD, and other motors. Bearing device
【０００２】[0002]
【従来の技術】例えばＶＴＲやテープストリーマ用のド
ラムスピンドルモータには、そのスピンドルを支承する
軸受として、従来、図１３に示すような軸受装置が組み
込まれている。この軸受装置はスピンドルモータのスピ
ンドルＳを支承する一対の転がり軸受１１，１１と、こ
れらの転がり軸受１１，１１を同一軸線上に保持する円
筒状のハウジング１２とから構成されている。2. Description of the Related Art For example, a drum spindle motor for a VTR or a tape streamer conventionally incorporates a bearing device as shown in FIG. 13 as a bearing for supporting the spindle. This bearing device is composed of a pair of rolling bearings 11, 11 for supporting a spindle S of a spindle motor, and a cylindrical housing 12 for holding these rolling bearings 11, 11 on the same axis.
【０００３】ハウジング１２は転がり軸受１１の外径面
と密嵌する内面を有しており、このハウジング１２の内
面には、図１４に示すような段部１３が形成されてい
る。なお、転がり軸受１１は外輪１１ａ、内輪１１ｂ、
転動体１１ｃ、保持器１１ｄ等から構成されている。こ
のような軸受装置は、転がり軸受１１の外輪１１ａをハ
ウジング１２内に嵌め込むと外輪１１ａの端面がハウジ
ング１２の内面に形成された段部１３に突き当たり、外
輪１１ａの端面がハウジング１２内に位置決めされるた
め、転がり軸受１１とハウジング１２との組付けを容易
に行なうことができるという利点を有している。The housing 12 has an inner surface closely fitted to the outer diameter surface of the rolling bearing 11, and a step portion 13 as shown in FIG. 14 is formed on the inner surface of the housing 12. The rolling bearing 11 includes an outer ring 11a, an inner ring 11b,
The rolling element 11c and the cage 11d are included. In such a bearing device, when the outer ring 11a of the rolling bearing 11 is fitted into the housing 12, the end surface of the outer ring 11a abuts on the step portion 13 formed on the inner surface of the housing 12, and the end surface of the outer ring 11a is positioned in the housing 12. Therefore, there is an advantage that the rolling bearing 11 and the housing 12 can be easily assembled.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、上述し
た従来の軸受装置にあっては、外輪１１ａの端面を段部
１３に突き当てたときに外輪１１ａが半径方向に僅かで
も傾くと軸受全体が傾いてしまい、その結果、軸芯に対
してハウジングがラジアル方向に偏芯して振れ周るた
め、回転精度を低下させるという問題点を有していた。
また、外輪１１ａが半径方向に傾かないように段部１３
を高精度に研削加工する必要があることから、コストの
低減を図ることが困難であった。However, in the above-described conventional bearing device, when the outer ring 11a is slightly tilted in the radial direction when the end surface of the outer ring 11a is abutted against the step portion 13, the entire bearing tilts. As a result, the housing eccentrically oscillates in the radial direction with respect to the shaft center, which causes a problem that rotational accuracy is reduced.
Further, the step portion 13 is arranged so that the outer ring 11a does not tilt in the radial direction.
It is difficult to reduce the cost because it is necessary to perform high precision grinding.
【０００５】本発明は上記の問題点に鑑みてなされたも
のであり、その目的とするところは、回転精度の向上と
コストの低減を図ることのできる軸受装置を提供するこ
とにある。The present invention has been made in view of the above problems, and an object of the present invention is to provide a bearing device capable of improving the rotational accuracy and reducing the cost.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するため
に、本発明のうち請求項１の発明は、スピンドルを支承
する一対の転がり軸受と、これらの転がり軸受を同一軸
上に保持する筒状のハウジングとを有し、前記ハウジン
グの内面に前記転がり軸受を嵌合保持した軸受装置にお
いて、軸受の中心軸線と接触角延長線との交点を通り、
且つ前記転がり軸受の軸方向に対して直角なラジアル平
面と前記転がり軸受の外輪外径面とが交差する部位に、
前記ハウジングの嵌合部を設けたことを特徴とする。In order to achieve the above object, a first aspect of the present invention provides a pair of rolling bearings for supporting a spindle, and a cylinder for holding these rolling bearings on the same shaft. In a bearing device in which the rolling bearing is fitted and held on the inner surface of the housing, passing through the intersection of the center axis of the bearing and the contact angle extension line,
And at the site where the radial plane perpendicular to the axial direction of the rolling bearing and the outer ring outer diameter surface of the rolling bearing intersect.
It is characterized in that a fitting portion of the housing is provided.
【０００７】請求項２の発明は、請求項１の発明に係る
軸受装置において、前記ハウジングの内面に前記転がり
軸受の外輪端面と当接する段部を設けるとともに、前記
ハウジングの両端側に軸受外径との嵌合部を設け、前記
嵌合部と前記段部とのハウジング内面を前記転がり軸受
の外径よりも大径に形成したことを特徴とする。請求項
３の発明は、スピンドルを支承する一対の転がり軸受
と、これらの転がり軸受を同一軸上に嵌合保持した軸受
装置において、軸受の中心軸線と接触角延長線との交点
を通り、且つ前記転がり軸受の軸方向に対して直角なラ
ジアル平面と前記転がり軸受の内輪内径面とが交差する
部位に、前記軸との嵌合部を設けたことを特徴とする。According to a second aspect of the present invention, in the bearing device according to the first aspect of the present invention, a step portion is provided on the inner surface of the housing for contacting the outer ring end surface of the rolling bearing, and the outer diameter of the bearing is provided on both end sides of the housing. And an inner surface of the housing between the fitting portion and the step portion is formed to have a diameter larger than an outer diameter of the rolling bearing. According to a third aspect of the present invention, in a pair of rolling bearings that support a spindle and a bearing device in which these rolling bearings are fitted and held on the same shaft, the bearing axis passes through the intersection of the central axis of the bearing and the contact angle extension line, and A fitting portion for the shaft is provided at a portion where a radial plane perpendicular to the axial direction of the rolling bearing intersects with an inner diameter surface of the inner ring of the rolling bearing.
【０００８】請求項４の発明は、請求項３の発明に係る
軸受装置において、軸受の中心軸線と接触角延長線との
交点を通り、且つ前記転がり軸受の軸方向に対して直角
なラジアル平面と前記転がり軸受の内輪内径面とが交差
する部位に、前記軸との嵌合部を設け、前記嵌合部から
玉側軸外径部に、前記転がり軸受の内輪内径部よりも径
の小さい縮径部を設けたことを特徴とする。According to a fourth aspect of the invention, in the bearing device according to the third aspect of the invention, a radial plane passing through the intersection of the central axis of the bearing and the contact angle extension line and perpendicular to the axial direction of the rolling bearing. And a portion for fitting with the shaft is provided at a portion where the inner ring inner diameter surface of the rolling bearing intersects, and the diameter is smaller than the inner ring inner diameter portion of the rolling bearing from the fitting portion to the ball side shaft outer diameter portion. It is characterized in that a reduced diameter portion is provided.
【０００９】請求項５の発明は、請求項１〜４の発明に
係る軸受装置において、前記転がり軸受が深溝玉軸受で
あることを特徴とする。請求項６の発明は、請求項１〜
４の発明に係る軸受装置において、前記転がり軸受がア
ンギュラ玉軸受であることを特徴とする。このような構
成であると、外輪が軸心に対し傾いてもハウジングと外
輪外面との嵌合部では偏心が極小となることから、軸心
に対してハウジングが偏芯して振れ周ることがない。ま
た、ハウジングに対して、軸心が傾くこともない。According to a fifth aspect of the present invention, in the bearing device according to the first to fourth aspects of the present invention, the rolling bearing is a deep groove ball bearing. The invention of claim 6 relates to claims 1 to
In the bearing device according to the invention of No. 4, the rolling bearing is an angular ball bearing. With such a configuration, even if the outer ring is tilted with respect to the axis, the eccentricity is minimized at the fitting portion between the housing and the outer surface of the outer ring. There is no. Further, the axis does not tilt with respect to the housing.
【００１０】このことから、外輪が軸心に対して傾かな
いように段部を高精度の研削加工しなくてもよいので、
コストの低減を図ることができる。本発明に係る軸受装
置において、スピンドルを支承する一対の転がり軸受と
して、玉軸受を好適に使用することができる。また、本
発明に係る軸受装置において、玉軸受の中心軸線と接触
角延長線との交点を通り且つ玉軸受の軸方向に対して直
角なラジアル平面と玉軸受の外径面とが交差する部位
に、ハウジングと外輪外径との嵌合部を設けることによ
り、外輪に軸心に対する傾きがあってもハウジングが半
径方向に偏心することがほとんどないので、軸を固定し
てハウジングを回転させた場合にハウジングの回転振れ
を最小限に抑えることができる。From this, it is not necessary to grind the step portion with high precision so that the outer ring does not tilt with respect to the axis.
The cost can be reduced. In the bearing device according to the present invention, a ball bearing can be preferably used as the pair of rolling bearings that support the spindle. Further, in the bearing device according to the present invention, a portion where the radial plane passing through the intersection of the central axis of the ball bearing and the contact angle extension line and perpendicular to the axial direction of the ball bearing intersects the outer diameter surface of the ball bearing. By providing a fitting portion between the housing and the outer diameter of the outer ring, the housing is rarely eccentric in the radial direction even if the outer ring is tilted with respect to the axial center, so the shaft is fixed and the housing is rotated. In this case, rotational runout of the housing can be minimized.
【００１１】また、玉軸受の中心軸線と接触角延長線と
の交点を通り、且つ前記玉軸受の軸方向に対して直角な
ラジアル平面と前記玉軸受の内輪内径面とが交差する部
位に、軸との嵌合部を設け、前記嵌合部から玉側軸外径
部に、前記内輪内径よりも径の小さい縮径部を設けるこ
とにより、軸心に対し内輪が傾いて固定されても、内輪
内径面との嵌合部では回転中心に対する偏心が極小にな
り、外輪を固定して軸を回転させたとき軸が振れ周るこ
とがない。Further, at a portion where a radial plane passing through the intersection of the central axis of the ball bearing and the contact angle extension line and perpendicular to the axial direction of the ball bearing intersects with the inner diameter surface of the inner ring of the ball bearing, Even if the inner ring is inclined and fixed with respect to the shaft center, by providing a fitting portion with the shaft and providing a reduced diameter portion having a diameter smaller than the inner diameter of the inner ring from the fitting portion to the ball-side shaft outer diameter portion. The eccentricity with respect to the center of rotation is minimal at the fitting portion with the inner ring inner diameter surface, and the shaft does not run around when the outer ring is fixed and the shaft is rotated.
【００１２】[0012]
【発明の実施の形態】以下、本発明の実施の形態を図面
に基づいて説明する。図１は本発明の第１の実施形態に
係る軸受装置の軸方向断面図で、図２は同実施形態に係
る軸受装置の要部を示す断面図である。図１において、
軸受装置１０はスピンドルモータのスピンドルＳを支承
する一対の深溝玉軸受１１，１１と、これらの玉軸受１
１，１１を同一軸線上に支持する円筒状のハウジング１
２とから構成されている。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is an axial sectional view of a bearing device according to a first embodiment of the present invention, and FIG. 2 is a sectional view showing a main part of the bearing device according to the same embodiment. In FIG.
The bearing device 10 includes a pair of deep groove ball bearings 11, 11 for supporting a spindle S of a spindle motor, and these ball bearings 1.
Cylindrical housing 1 for supporting 1 and 11 on the same axis
2 and.
【００１３】ハウジング１２は転がり軸受１１の外径面
と密嵌する内面を有しており、このハウジング１２の内
面には、図２に示すような段部１３が形成されている。
なお、玉軸受１１は外輪１１ａ、内輪１１ｂ、転動体１
１ｃ、保持器１１ｄ等から構成されている。ハウジング
１２の嵌合部１２ａ，１２ａは外輪１１ａの外径面にそ
れぞれ嵌合しており、これら嵌合部１２ａ，１２ａと段
部１３との間のハウジング内面１２ｃは、図２に示すよ
うに、玉軸受１１の外径すなわち外輪１１ａの外径より
も大径に形成されている。The housing 12 has an inner surface that closely fits the outer diameter surface of the rolling bearing 11, and a step portion 13 as shown in FIG. 2 is formed on the inner surface of the housing 12.
The ball bearing 11 includes an outer ring 11a, an inner ring 11b, and rolling elements 1.
1c, a retainer 11d and the like. The fitting portions 12a, 12a of the housing 12 are fitted to the outer diameter surface of the outer ring 11a, respectively, and the housing inner surface 12c between the fitting portions 12a, 12a and the step portion 13 is as shown in FIG. The outer diameter of the ball bearing 11, that is, the outer diameter of the outer ring 11a, is formed larger.
【００１４】また、ハウジング１２の嵌合部１２ａ，１
２ａは、玉軸受１１の中心軸線Ａと接触角延長線Ｌとの
交点Ｐを通り且つ玉軸受１１の軸方向に対して直角なラ
ジアル平面Ｒが玉軸受１１の外輪外径面１１ｅと交差す
る部位に設けられている。なお、本実施形態では軸径：
２ｍｍ、軸受幅：３ｍｍの軸受１１に対し、段部１３と
突き当たる側の外輪端面から２．１ｍｍ程度の位置をラ
ジアル平面Ｒが玉軸受１１の外輪外径面１１ｅと交差す
る位置とし、ハウジング１２の嵌合部１２ａの軸方向長
さを０．６ｍｍ程度としている。Also, the fitting portions 12a, 1 of the housing 12
In 2a, a radial plane R passing through an intersection P between the central axis A of the ball bearing 11 and the contact angle extension line L and perpendicular to the axial direction of the ball bearing 11 intersects the outer ring outer diameter surface 11e of the ball bearing 11. It is provided in the part. In the present embodiment, the shaft diameter:
With respect to the bearing 11 having a width of 2 mm and a bearing width of 3 mm, the radial plane R intersects with the outer ring outer diameter surface 11e of the ball bearing 11 at a position of about 2.1 mm from the outer ring end surface that abuts the step portion 13, and the housing 12 The axial length of the fitting portion 12a is about 0.6 mm.
【００１５】なお、本実施形態に係る軸受装置１０を組
立てる場合は、軸Ｓに図中左側の軸受１１を固定し、ハ
ウジング１２を図中右側から左方へ動かし、外輪端面を
段部１３に突き当てる。そして、右側の軸受１１をハウ
ジング１２の右方より嵌め込み、段部１３に外輪１１ａ
を突き当てた後、内輪１１ｂの押圧量により予圧をコン
トロールして組立てられる。When assembling the bearing device 10 according to the present embodiment, the bearing 11 on the left side in the figure is fixed to the shaft S, the housing 12 is moved from the right side to the left side in the figure, and the outer ring end surface is formed on the step portion 13. Strike. Then, the bearing 11 on the right side is fitted from the right side of the housing 12, and the outer ring 11a is attached to the step portion 13.
After abutting against, the pre-load is controlled by the pressing amount of the inner ring 11b for assembly.
【００１６】このような構成において、玉軸受１１の外
輪１１ａをハウジング１２内に嵌め込むと、図２に示す
ように、外輪１１ａの外径面とハウジング１１の内面１
２ｃとの間に環状間隙１４が形成される。これにより、
外輪１１ａが軸心に対しある程度傾いても嵌合部では回
転軸心に対して偏心が極小となることから、軸心に対し
てハウジングがラジアル方向に偏芯して振れ周るような
ことがなくなり、回転精度の向上を図ることができる。
また、外輪１１ａが軸心に対し傾かないように段部１３
を高精度に研削加工する必要がないので、コストの低減
を図ることができる。In such a structure, when the outer ring 11a of the ball bearing 11 is fitted into the housing 12, the outer diameter surface of the outer ring 11a and the inner surface 1 of the housing 11 are fitted, as shown in FIG.
An annular gap 14 is formed between it and 2c. This allows
Even if the outer ring 11a is tilted to some extent with respect to the shaft center, the eccentricity with respect to the rotation shaft center is minimized at the fitting portion, so that the housing may eccentrically eccentrically rotate around the shaft center. It is possible to improve the rotation accuracy.
Further, the step portion 13 is arranged so that the outer ring 11a does not tilt with respect to the axis.
Since it is not necessary to perform the grinding process with high accuracy, the cost can be reduced.
【００１７】さらに、本実施形態では玉軸受１１の中心
軸線Ａと接触角延長線Ｌとの交点Ｐを通り且つ玉軸受１
１の軸方向に対して直角なラジアル平面Ｒが玉軸受１１
の外輪外径面１１ｅと交差する部位にハウジング１２の
嵌合部１２ａ，１２ａを設けたことにより、外輪１１ａ
に傾きがあってもハウジング１２が傾くことが極小であ
るため、スピンドルＳを固定してハウジング１２を回転
させた場合のハウジング１２の回転振れを最小限に抑え
ることができる。Further, in this embodiment, the ball bearing 1 passes through the intersection P between the central axis A of the ball bearing 11 and the contact angle extension line L.
1 is a radial plane R perpendicular to the axial direction of the ball bearing 11
Since the fitting portions 12a, 12a of the housing 12 are provided at the portion intersecting the outer ring outer diameter surface 11e of the outer ring 11a
Even if the housing 12 is tilted, the housing 12 is minimally tilted. Therefore, when the housing 12 is rotated with the spindle S fixed, the rotational shake of the housing 12 can be minimized.
【００１８】なお、本発明は上述した実施形態に限定さ
れるものではない。たとえば、図３及び図４に示す第２
の実施形態のように、玉軸受１１の内輪１１ｂと嵌合す
る軸部１５の両端に内輪１１ｂの内径よりも径の小さい
縮径部１６をスピンドルＳに設けても良い。このような
構成によると、内輪１１ｂの内径面と縮径部１６との間
に形成された環状間隙１７（図４参照）によって内輪１
１ｂの傾きが許容されるので、内輪１１ｂの傾きによる
影響を低減することができる。The present invention is not limited to the above embodiment. For example, the second shown in FIGS.
As in the above embodiment, the spindle S may be provided with the reduced diameter portions 16 having a diameter smaller than the inner diameter of the inner ring 11b at both ends of the shaft portion 15 fitted with the inner ring 11b of the ball bearing 11. With such a configuration, the inner ring 1 is formed by the annular gap 17 (see FIG. 4) formed between the inner diameter surface of the inner ring 11b and the reduced diameter portion 16.
Since the inclination of 1b is allowed, the influence of the inclination of the inner ring 11b can be reduced.
【００１９】また、図５及び図６に示す第３の実施形態
のように、スピンドルＳを支承する一対の玉軸受１１，
１１間にコイルばね１８を設け、このコイルばね１８に
よって玉軸受１１の外輪１１ｂにアキシアル方向の予圧
を付与するようにしても良い。さらに、図７及び図８に
示す第４の実施形態のように、ハウジング１２の両端部
に接着剤注入孔１９を設け、この接着剤注入孔１９から
ハウジング１２の内面１２ｃと外輪１１ａの外径面との
間に形成された環状間隙１４の、軸方向の一方を軸受の
中心線と接触角延長線との交点を通り、且つ前記玉軸受
の軸方向に対して直角なラジアル平面と前記玉軸受の外
径面と交差する位置を、締め代を持たせ嵌合し、他方を
接着剤が流失してしまわない程度の絞りを設け、環状間
隙１４に接着剤を注入して外輪１１ａとハウジング１２
とを接着剤で固定するようにしてもよい。Further, as in the third embodiment shown in FIGS. 5 and 6, a pair of ball bearings 11, which support the spindle S,
A coil spring 18 may be provided between 11 and the coil spring 18 may apply a preload in the axial direction to the outer ring 11b of the ball bearing 11. Further, as in the fourth embodiment shown in FIGS. 7 and 8, adhesive injection holes 19 are provided at both ends of the housing 12, and the inner diameter 12 c of the housing 12 and the outer diameter of the outer ring 11 a are provided from the adhesive injection holes 19. A radial plane that passes through the intersection of the center line of the bearing and the extension line of the contact angle in one axial direction of the annular gap 14 formed between the ball gap and the radial plane that is perpendicular to the axial direction of the ball bearing; A position that intersects the outer diameter surface of the bearing is fitted with a tightening allowance, and the other is provided with a throttle to the extent that the adhesive does not flow away. The adhesive is injected into the annular gap 14 and the outer ring 11a and the housing. 12
And may be fixed with an adhesive.
【００２０】締め代による保持力だけでは足りない場合
でも、接着による補強ができる。また、図７及び図８に
示す第４の実施形態では内輪側も、予め接着剤を軸に設
けた縮径部１６に塗布しておき、縮径部１６の軸方向一
方を軸受の中心線と接触角延長線との交点を通り、且つ
前記玉軸受の軸方向に対して直角なラジアル平面と前記
玉軸受の内径面と交差する位置を、締め代を持たせ嵌合
し、他方を接着剤が流失してしまわない程度の絞りを設
け、内輪１１ｂと軸とを接着剤で固定するようにしても
よい。Even if the holding force due to the tightening margin is not sufficient, reinforcement can be provided by adhesion. Further, in the fourth embodiment shown in FIGS. 7 and 8, the inner ring side is also preliminarily coated with adhesive on the reduced diameter portion 16 provided on the shaft, and one side of the reduced diameter portion 16 in the axial direction is the center line of the bearing. And the contact angle extension line, and the radial plane perpendicular to the axial direction of the ball bearing and the position intersecting the inner diameter surface of the ball bearing are fitted with a tightening allowance, and the other is bonded. It is also possible to provide a throttle to such an extent that the agent is not washed away, and fix the inner ring 11b and the shaft with an adhesive.
【００２１】締め代による保持力だけでは足りない場合
でも、接着による補強ができる。また、図９及び図１０
に示す第５の実施形態のように、ハウジング１２にビデ
オテープ等の磁気記録テープを走行駆動するドラム２０
を一体に設けても良い。図５及び図６に示した第３の実
施形態では、玉軸受１１の内輪１１ｂと軸Ｓとが嵌合す
る嵌合部１５の両側に内輪１１ｂの内径よりも径の小さ
い縮径部１６を設けたが、図１１に示す第６の実施形態
のように、縮径部１６を嵌合部１５のハウジング端部と
反対側（軸Ｓの中央側）のみに設けてもよい。なお、第
６の実施形態に係る軸受装置はハウジング１２を温めて
おき、そこに予め軸Ｓと軸受１１とコイルばね１８がサ
ブ組立されたものを挿入して組立てられる。Even if the holding force due to the tightening margin is not sufficient, reinforcement can be provided by adhesion. Also, FIG. 9 and FIG.
A drum 20 for driving a magnetic recording tape such as a video tape in the housing 12 as in the fifth embodiment shown in FIG.
May be integrally provided. In the third embodiment shown in FIGS. 5 and 6, a reduced diameter portion 16 having a diameter smaller than the inner diameter of the inner ring 11b is provided on both sides of the fitting portion 15 where the inner ring 11b of the ball bearing 11 and the shaft S fit. However, as in the sixth embodiment shown in FIG. 11, the reduced diameter portion 16 may be provided only on the side opposite to the housing end portion of the fitting portion 15 (the center side of the shaft S). The bearing device according to the sixth embodiment is assembled by warming the housing 12 and inserting therein the shaft S, the bearing 11 and the coil spring 18 which are sub-assembled in advance.
【００２２】また、図１２に示す第７の実施形態のよう
に、ハウジング１２の端部に外輪１１ａの外径よりも径
の大きい内径面１２ｄを設けることにより、玉軸受１１
をハウジング１２内に容易に組み込むことができる。な
お、第１乃至第４の実施形態ではスピンドルＳを支承す
る転がり軸受として内輪１１ｂを有する深溝玉軸受を使
用したが、図９及び図１０に示す第５の実施形態のよう
に、内輪を有しない深溝玉軸受を用いてもよい。さら
に、上述した各実施形態ではスピンドルＳを支承する転
がり軸受として深溝玉軸受１１を用いたが、これの代わ
りにアンギュラ玉軸受を用いてもよい。Further, as in the seventh embodiment shown in FIG. 12, the ball bearing 11 is provided with an inner diameter surface 12d having a diameter larger than the outer diameter of the outer ring 11a at the end of the housing 12.
Can be easily incorporated into the housing 12. In the first to fourth embodiments, the deep groove ball bearing having the inner ring 11b is used as the rolling bearing that supports the spindle S. However, as in the fifth embodiment shown in FIGS. 9 and 10, the inner ring has the inner ring 11b. Alternatively, a deep groove ball bearing may be used. Furthermore, in each of the above-described embodiments, the deep groove ball bearing 11 is used as the rolling bearing that supports the spindle S, but an angular ball bearing may be used instead of this.
【００２３】[0023]
【発明の効果】以上説明したように、本発明によれば、
外輪が軸心に対し傾いてもハウジングと外輪外面との嵌
合部では偏心が極小となることから、軸心に対してハウ
ジングが偏芯して振れ周ることがない。また、ハウジン
グに対して、軸心が傾くこともない。従って、外輪が軸
心に対して傾かないように段部を高精度研削加工しなく
てもよいので、コストの低減を図ることができる。As described above, according to the present invention,
Even if the outer ring is tilted with respect to the shaft center, the eccentricity is minimized at the fitting portion between the housing and the outer surface of the outer ring, so that the housing does not eccentrically rotate about the shaft center. Further, the axis does not tilt with respect to the housing. Therefore, it is not necessary to grind the stepped portion with high precision so that the outer ring is not tilted with respect to the axis, so that the cost can be reduced.
【図１】本発明の第１の実施形態に係る軸受装置の軸方
向断面図である。FIG. 1 is an axial sectional view of a bearing device according to a first embodiment of the present invention.
【図２】図１に示す軸受装置の一部拡大断面図である。FIG. 2 is a partially enlarged cross-sectional view of the bearing device shown in FIG.
【図３】本発明の第２の実施形態に係る軸受装置の軸方
向断面図である。FIG. 3 is an axial sectional view of a bearing device according to a second embodiment of the present invention.
【図４】図３に示す軸受装置の一部拡大断面図である。4 is a partially enlarged cross-sectional view of the bearing device shown in FIG.
【図５】本発明の第３の実施形態に係る軸受装置の軸方
向断面図である。FIG. 5 is an axial sectional view of a bearing device according to a third embodiment of the present invention.
【図６】図５に示す軸受装置の一部拡大断面図である。6 is a partially enlarged cross-sectional view of the bearing device shown in FIG.
【図７】本発明の第４の実施形態に係る軸受装置の軸方
向断面図である。FIG. 7 is an axial sectional view of a bearing device according to a fourth embodiment of the present invention.
【図８】図７に示す軸受装置の一部拡大断面図である。FIG. 8 is a partially enlarged sectional view of the bearing device shown in FIG.
【図９】本発明の第５の実施形態に係る軸受装置の軸方
向断面図である。FIG. 9 is an axial sectional view of a bearing device according to a fifth embodiment of the present invention.
【図１０】図９に示す軸受装置の一部拡大断面図であ
る。10 is a partially enlarged cross-sectional view of the bearing device shown in FIG.
【図１１】本発明の第６の実施形態に係る軸受装置の軸
方向断面図である。FIG. 11 is an axial sectional view of a bearing device according to a sixth embodiment of the present invention.
【図１２】本発明の第７の実施形態に係る軸受装置の軸
方向断面図である。FIG. 12 is an axial sectional view of a bearing device according to a seventh embodiment of the present invention.
【図１３】従来の軸受装置の軸方向断面図である。FIG. 13 is an axial sectional view of a conventional bearing device.
【図１４】図１３に示す軸受装置の一部拡大断面図であ
る。14 is a partially enlarged cross-sectional view of the bearing device shown in FIG.
Ｓ スピンドル １１ 深溝玉軸受 １１ａ 外輪 １１ｂ 内輪 １１ｃ 球状転動体 １１ｄ 保持器 １２ ハウジング １２ｃ 内面 １３ 段部 １４ 環状間隙 １５ 軸部 １６ 縮径部 S spindle 11 Deep groove ball bearings 11a outer ring 11b inner ring 11c Spherical rolling element 11d cage 12 housing 12c inner surface 13 steps 14 annular gap 15 Shaft 16 Reduced diameter part
Claims (6)
と、これらの転がり軸受を同一軸上に保持する筒状のハ
ウジングとを有し、前記ハウジングの内面に前記転がり
軸受を嵌合保持した軸受装置において、軸受の中心軸線
と接触角延長線との交点を通り、且つ前記転がり軸受の
軸方向に対して直角なラジアル平面と前記転がり軸受の
外輪外径面とが交差する部位に、前記ハウジングの嵌合
部を設けたことを特徴とする軸受装置。1. A bearing device having a pair of rolling bearings for supporting a spindle, and a cylindrical housing for holding these rolling bearings on the same shaft, wherein the rolling bearing is fitted and held on an inner surface of the housing. In the above, in the portion where the radial plane that passes through the intersection of the central axis of the bearing and the contact angle extension line and is orthogonal to the axial direction of the rolling bearing and the outer ring outer diameter surface of the rolling bearing intersect, A bearing device having a fitting portion.
の外輪端面と当接する段部を設けて構成される軸受装置
において、 前記ハウジングの両端側に軸受外径との嵌合部を設け、
前記嵌合部と前記段部とのハウジング内面を前記転がり
軸受の外径よりも大径に形成したことを特徴とする請求
項１記載の軸受装置。2. A bearing device comprising an inner surface of the housing provided with a step portion that abuts an outer ring end surface of the rolling bearing, wherein both ends of the housing are provided with fitting portions with a bearing outer diameter,
The bearing device according to claim 1, wherein an inner surface of the housing between the fitting portion and the step portion is formed to have a diameter larger than an outer diameter of the rolling bearing.
と、これらの転がり軸受を同一軸上に嵌合保持した軸受
装置において、軸受の中心軸線と接触角延長線との交点
を通り、且つ前記転がり軸受の軸方向に対して直角なラ
ジアル平面と前記転がり軸受の内輪内径面とが交差する
部位に、前記軸との嵌合部を設けたことを特徴とする軸
受装置。3. A pair of rolling bearings for supporting a spindle, and a bearing device in which these rolling bearings are fitted and held on the same shaft, wherein the rolling bearing passes through the intersection of the central axis of the bearing and the extension line of the contact angle. A bearing device, wherein a fitting portion for the shaft is provided at a portion where a radial plane perpendicular to the axial direction of the bearing intersects with an inner ring inner diameter surface of the rolling bearing.
おいて、軸受の中心軸線と接触角延長線との交点を通
り、且つ前記転がり軸受の軸方向に対して直角なラジア
ル平面と前記転がり軸受の内輪内径面とが交差する部位
に、前記軸との嵌合部を設け、前記嵌合部から玉側軸外
径部に、前記転がり軸受の内輪内径部よりも径の小さい
縮径部を設けたことを特徴とする請求項３記載の軸受装
置。4. A bearing device fitted and held on the same shaft, wherein a radial plane passing through an intersection of a central axis of the bearing and a contact angle extension line and perpendicular to the axial direction of the rolling bearing, and the rolling element. A fitting portion with the shaft is provided at a portion where the inner ring inner diameter surface of the bearing intersects, and a reduced diameter portion having a diameter smaller than the inner ring inner diameter portion of the rolling bearing is provided from the fitting portion to the ball side shaft outer diameter portion. The bearing device according to claim 3, further comprising:
求項１〜４のいずれか１項記載の軸受装置。5. The bearing device according to claim 1, wherein the rolling bearing is a deep groove ball bearing.
ある請求項１〜４のいずれか１項記載の軸受装置。6. The bearing device according to claim 1, wherein the rolling bearing is an angular ball bearing.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001288548A JP2003097576A (en) | 2001-09-21 | 2001-09-21 | Bearing device |
| PCT/JP2002/009634 WO2003027523A1 (en) | 2001-09-21 | 2002-09-19 | Bearing device |
| CNB028185358A CN1293320C (en) | 2001-09-21 | 2002-09-19 | Bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001288548A JP2003097576A (en) | 2001-09-21 | 2001-09-21 | Bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003097576A true JP2003097576A (en) | 2003-04-03 |
Family
ID=19111176
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001288548A Pending JP2003097576A (en) | 2001-09-21 | 2001-09-21 | Bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003097576A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005043945A1 (en) * | 2005-09-15 | 2007-03-22 | Schaeffler Kg | Roller bearing for machine tool spindle has ring with higher coefficient of thermal expansion than outer ring |
| DE102005043954A1 (en) * | 2005-09-15 | 2007-03-22 | Schaeffler Kg | Radial roller bearing, especially for machine tool's main spindle, has tension ring which radially constricts running track and consists of material with higher thermal expansion coefficient than material of outer race |
| JP2007081109A (en) * | 2005-09-14 | 2007-03-29 | Jtekt Corp | Guide roller device, and its manufacturing method |
| JP2010196707A (en) * | 2009-02-24 | 2010-09-09 | Dyson Technology Ltd | Rotor assembly |
| US8864460B2 (en) | 2011-08-26 | 2014-10-21 | Dyson Technology Limited | Bearing assembly |
| JP2015094446A (en) * | 2013-11-13 | 2015-05-18 | 株式会社ジェイテクト | Rotating device and steering device for vehicle |
| US9624940B2 (en) | 2009-02-24 | 2017-04-18 | Dyson Technology Limited | Rotor assembly |
| CN107366686A (en) * | 2017-07-24 | 2017-11-21 | 南通山口精工机电有限公司 | A kind of axle and bearing jointing structure |
-
2001
- 2001-09-21 JP JP2001288548A patent/JP2003097576A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007081109A (en) * | 2005-09-14 | 2007-03-29 | Jtekt Corp | Guide roller device, and its manufacturing method |
| JP4517991B2 (en) * | 2005-09-14 | 2010-08-04 | 株式会社ジェイテクト | Guide roller device and guide roller device manufacturing method |
| DE102005043945A1 (en) * | 2005-09-15 | 2007-03-22 | Schaeffler Kg | Roller bearing for machine tool spindle has ring with higher coefficient of thermal expansion than outer ring |
| DE102005043954A1 (en) * | 2005-09-15 | 2007-03-22 | Schaeffler Kg | Radial roller bearing, especially for machine tool's main spindle, has tension ring which radially constricts running track and consists of material with higher thermal expansion coefficient than material of outer race |
| JP2010196707A (en) * | 2009-02-24 | 2010-09-09 | Dyson Technology Ltd | Rotor assembly |
| US9624940B2 (en) | 2009-02-24 | 2017-04-18 | Dyson Technology Limited | Rotor assembly |
| US8864460B2 (en) | 2011-08-26 | 2014-10-21 | Dyson Technology Limited | Bearing assembly |
| JP2015094446A (en) * | 2013-11-13 | 2015-05-18 | 株式会社ジェイテクト | Rotating device and steering device for vehicle |
| CN107366686A (en) * | 2017-07-24 | 2017-11-21 | 南通山口精工机电有限公司 | A kind of axle and bearing jointing structure |
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