JP2563692Y2 - Double row angular contact ball bearing device - Google Patents
Double row angular contact ball bearing deviceInfo
- Publication number
- JP2563692Y2 JP2563692Y2 JP4157092U JP4157092U JP2563692Y2 JP 2563692 Y2 JP2563692 Y2 JP 2563692Y2 JP 4157092 U JP4157092 U JP 4157092U JP 4157092 U JP4157092 U JP 4157092U JP 2563692 Y2 JP2563692 Y2 JP 2563692Y2
- Authority
- JP
- Japan
- Prior art keywords
- inner ring
- shaft member
- peripheral surface
- ring
- 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.)
- Expired - Fee Related
Links
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
- F16C43/00—Assembling bearings
- F16C43/04—Assembling rolling-contact bearings
- F16C43/06—Placing rolling bodies in cages or bearings
- F16C43/08—Placing rolling bodies in cages or bearings by deforming the cages or the races
- F16C43/086—Placing rolling bodies in cages or bearings by deforming the cages or the races by plastic deformation of the race
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
- F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
- F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
- F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles 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
- F16C33/588—Races of sheet metal
-
- 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
- F16C33/64—Special methods of manufacture
-
- 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
- F16C2370/00—Apparatus relating to physics, e.g. instruments
- F16C2370/12—Hard disk drives or the like
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Manufacturing & Machinery (AREA)
- Support Of The Bearing (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本考案は、複列アンギュラコンタ
クト玉軸受装置の改良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improved double-row angular contact ball bearing device.
【０００２】[0002]
【従来の技術】従来、例えば磁気ハードディスク装置
(以下、ＨＤＤと記す。）では、記録ディスクを回転さ
せるためのスピンドルモータ用軸受やスイングアームを
支持するためのピボット用軸受が使用されている。上記
ＨＤＤでは、近年のダウンサイズ化の要請から、外径
１．８インチ (約４６ｍｍ）の記録ディスクが用いられ
ており、今後は、さらに外径１．３インチ (約３３ｍ
ｍ）程度のものも用いられることが予想される。2. Description of the Related Art Conventionally, for example, a magnetic hard disk drive
(Hereinafter referred to as HDD), a spindle motor bearing for rotating a recording disk and a pivot bearing for supporting a swing arm are used. In the HDD, a recording disk having an outer diameter of 1.8 inches (approximately 46 mm) is used in response to a recent demand for downsizing.
It is expected that those having a size of m) will be used.
【０００３】上記ダウンサイズ化に伴って、上記ＨＤＤ
を携帯用とするには、このＨＤＤに使用する軸受は、極
小化とともに、耐衝撃性も要求されるようになる。例え
ば、上記１．８インチの記録ディスク用軸受は、内径２
ｍｍ、外径５ｍｍ、幅２ｍｍ以下、上記１．３インチの
記録ディスク用軸受は、内径１ｍｍ、外径３ｍｍ、幅１
〜２ｍｍ以下が要求される。上記軸受が極小化すると、
各部品の加工や組立が従来の技術では対応が困難で、コ
ストアップにもなる。また、軸受の耐衝撃性にも限界が
ある。[0003] With the downsizing, the HDD
In order to make the HDD portable, the bearings used in the HDD are required to be miniaturized and have impact resistance. For example, the 1.8-inch recording disk bearing has an inner diameter of 2 inches.
mm, outer diameter 5 mm, width 2 mm or less, the above-mentioned 1.3 inch recording disk bearing has an inner diameter 1 mm, an outer diameter 3 mm, and a width 1
２2 mm or less is required. When the above bearings are minimized,
It is difficult to process and assemble each part with the conventional technology, and the cost increases. Also, there is a limit to the impact resistance of the bearing.
【０００４】上記要求に応えるものとして、図２に示す
ように、内輪１の環状曲部１ａ,１ａに、複列の玉３,３
をそれぞれ環状に配列して、油圧プレスローラ４によ
り、外輪２に環状凹部２ａを形成した複列アンギュラコ
ンタクト玉軸受装置が提案されている (特開平１−２１
０６１２号公報参照）。この複列アンギュラコンタクト
玉軸受装置は、上記油圧プレスローラによるプレス形成
時に、上記内輪１,外輪２と玉３間に予圧が与えられ
る。[0004] In order to meet the above demand, as shown in FIG. 2, double-row balls 3, 3 are attached to the annular curved portions 1 a, 1 a of the inner ring 1.
Are arranged annularly, and a double-row angular contact ball bearing device in which an annular recess 2a is formed in the outer race 2 by a hydraulic press roller 4 has been proposed (Japanese Patent Laid-Open No. 1-21).
No. 0612). In this double-row angular contact ball bearing device, a preload is applied between the inner ring 1, the outer ring 2 and the ball 3 during press forming by the hydraulic press roller.
【０００５】[0005]
【考案が解決しようとする課題】しかしながら、上記軸
受装置では、油圧プレスローラ４で予圧を与えるもので
あるから、予圧がばらつきやすいという問題がある。However, in the above bearing device, since the preload is applied by the hydraulic press roller 4, there is a problem that the preload tends to vary.
【０００６】そこで、本考案の目的は、適性な予圧を設
定できる複列アンギュラコンタクト玉軸受装置を提供す
ることにある。Accordingly, an object of the present invention is to provide a double-row angular contact ball bearing device capable of setting an appropriate preload.
【０００７】[0007]
【課題を解決するための手段】上記目的を達成するため
に、本考案は、内周面の軸方向の略中間部に、径方向内
側へ突出する環状凸部を有し、この環状凸部の両側の上
記内周面に軌道部を有するプレス板製の外輪と、上記外
輪の一方の軌道部の径方向内側に配置され、軸方向外側
外周に、軌道部を形成する湾曲肩部を有し、内周面に軸
部材に嵌合される嵌合部を有するプレス板製の第１内輪
と、上記外輪の他方の軌道部の径方向内側に配置され、
軸方向外側外周に、軌道部を形成する湾曲肩部を有し、
内周面に軸部材に隙間嵌めされる嵌合部を有するプレス
板製の第２内輪と、上記各内輪の各軌道部と上記外輪の
各軌道部との間に配置される複数の玉と、上記各玉を列
毎に保持する保持器とを備え、上記第２内輪は、上記軸
部材に対して隙間嵌めして取り付けられ、軸方向に予圧
付与した後に上記軸部材に接着固定されていることを特
徴としている。In order to achieve the above object, the present invention has an annular convex portion protruding radially inward at a substantially middle portion of the inner peripheral surface in the axial direction. An outer ring made of a pressed plate having a track portion on the inner peripheral surface on both sides of the outer ring, and a curved shoulder portion formed radially inside one of the track portions of the outer ring and forming a track portion on an outer periphery in the axial direction. A first inner ring made of a press plate having a fitting portion fitted to the shaft member on the inner peripheral surface; and a radially inner side of the other raceway portion of the outer ring,
On the outer periphery in the axial direction, there is a curved shoulder forming a track portion,
A second inner ring made of a press plate having a fitting portion which is fitted into the shaft member on the inner peripheral surface with a gap, and a plurality of balls arranged between each raceway portion of each inner race and each raceway portion of the outer race. A retainer for holding each of the balls for each row, wherein the second inner ring is attached to the shaft member by a clearance fit, and is adhesively fixed to the shaft member after applying a preload in the axial direction. It is characterized by having.
【０００８】[0008]
【作用】本考案によれば、外輪、内輪、玉及び保持器を
仮組みした後、第２内輪の嵌合部を軸部材に隙間嵌め
し、第２内輪の肩部に軸方向からたとえば重錘で荷重を
かけると第２内輪,玉,外輪,玉,第１内輪の順に力が伝え
られ、予圧が与えられ、油圧装置で予圧が与えられる従
来例と異なり、重量が一定の重錘で常に適性な予圧を設
定できるようになる。上記予圧を与えた後、上記第２内
輪と軸部材とを接着固定して、内輪の嵌め外れを防止す
る。According to the present invention, after the outer ring, the inner ring, the balls and the retainer are temporarily assembled, the fitting portion of the second inner ring is gap-fitted to the shaft member, and the shoulder of the second inner ring is axially weighted, for example. When a load is applied by the weight, the force is transmitted in the order of the second inner ring, the ball, the outer ring, the ball, and the first inner ring, and the preload is applied. Unlike the conventional example in which the preload is applied by the hydraulic device, the weight is constant. An appropriate preload can always be set. After the preload is applied, the second inner race and the shaft member are bonded and fixed to prevent the inner race from being disengaged.
【０００９】[0009]
【実施例】以下、本考案を図示の実施例により詳細に説
明する。図１に示すように、複列アンギュラコンタクト
玉軸受装置は、外輪１０と、一対の内輪１１Ａ,１１Ｂ
と、複列の玉１２,１２及び保持器１３,１３とで構成し
ている。１１Ａは第２内輪であり、１１Ｂは第１内輪で
ある。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the illustrated embodiments. As shown in FIG. 1, the double row angular contact ball bearing device includes an outer ring 10 and a pair of inner rings 11A and 11B.
And multiple rows of balls 12 and 12 and retainers 13 and 13. 11A is a second inner ring, and 11B is a first inner ring.
【００１０】上記外輪１０はステンレス鋼製の平板もし
くはパイプ材を素材としている。そして、上記外輪１０
は、内周面の略中間部に、プレス加工またはローリング
加工により、内方へ突出する環状凸部１０ａが形成され
ており、この環状凸部１０ａの両側の内周面に軌道部１
０ｂ,１０ｃが形成されている。The outer ring 10 is made of a stainless steel flat plate or pipe material. And, the outer ring 10
Is formed with an annular convex portion 10a projecting inward at a substantially middle portion of the inner peripheral surface by press working or rolling process, and a track portion 1 is provided on the inner peripheral surface on both sides of the annular convex portion 10a.
0b and 10c are formed.
【００１１】上記外輪１０は、外周面をハウジング１５
の穴に嵌合させ、この外輪１０の軌道部１０ｃ側の外端
部に一体的に形成したフランジ１０ｄを上記ハウジング
１５の端面に当接させて、軸方向を位置決めできるよう
にしている。上記外輪１０の環状凸部１０ａにより、外
輪１０の外周面には環状凹部１０ｅが形成され、この環
状凹部１０ｅに接着剤を充填すれば、ハウジング５の穴
に外輪１０を固定できる。The outer race 10 has an outer peripheral surface formed of a housing 15.
The flange 10d formed integrally with the outer end of the outer race 10 on the side of the raceway portion 10c is brought into contact with the end face of the housing 15 so that the axial direction can be positioned. An annular concave portion 10e is formed on the outer peripheral surface of the outer ring 10 by the annular convex portion 10a of the outer ring 10, and the outer ring 10 can be fixed to the hole of the housing 5 by filling the annular concave portion 10e with an adhesive.
【００１２】上記外輪１０は、必要に応じて、浸炭焼入
れなどの表面硬化処理を施し、軌道部１０ｂ,１０ｃの
疲労強度を向上させる。また、軌道部１０ｂ,１０ｃ
は、必要に応じて、研削、超仕上げ加工を行う。The outer race 10 is subjected to a surface hardening treatment such as carburizing and quenching, if necessary, to improve the fatigue strength of the raceways 10b and 10c. Also, the track portions 10b, 10c
Performs grinding and super finishing as necessary.
【００１３】上記第２内輪１１Ａ,第１内輪１１Ｂは、
上記外輪１０の各軌道部１０ｂ,１０ｃの内側に軸方向
の両側からそれぞれ嵌合される。この各内輪１１Ａ,１
１Ｂの軸方向外端外周には、湾曲肩部１１b ,１１b が
形成され、この湾曲肩部１１b ,１１b に軌道部１１ａ,
１１ａが形成されている。The second inner ring 11A and the first inner ring 11B are
The inner races 10b and 10c are fitted inside the races 10b and 10c from both sides in the axial direction. Each inner ring 11A, 1
Curved shoulders 11b, 11b are formed on the outer periphery of the outer end in the axial direction of 1B. Tracks 11a, 11b are formed on the curved shoulders 11b, 11b.
11a is formed.
【００１４】上記第２内輪１１Ａ,第１内輪１１Ｂの内
周面には、軸部材１４に隙間嵌めされる嵌合部１１ｃ,
１１ｃが形成されている。また、上記湾曲肩部１１ｂ,
１１ｂの湾曲央部１１e を上記軸部材１４に接触させな
いようにしている。On the inner peripheral surfaces of the second inner race 11A and the first inner race 11B, a fitting portion 11c which is clearance-fitted to the shaft member 14 is provided.
11c is formed. In addition, the curved shoulder 11b,
The curved central portion 11e of 11b is prevented from contacting the shaft member 14.
【００１５】上記各内輪１１Ａ,１１Ｂも、上記外輪１
０と同様の素材で加工し、必要に応じて表面処理や仕上
げ加工を行う。The inner races 11A and 11B are also connected to the outer race 1
Work with the same material as for No. 0, and perform surface treatment and finishing as needed.
【００１６】上記玉１２は、上記第２内輪１１Ａ,第１
内輪１１Ｂの各軌道部１１ａ,１１ａと上記外輪１０の
各軌道部１０ｂ,１０ｃとの間にそれぞれ配置され、各
玉１２は、保持器１３,１３により列毎に保持される。
この各保持器１３,１３は、組立てを容易にするため、
単体の状態で玉１２を組込んだとき、玉１２が脱落しな
いような寸法のポケット部を有することが好ましい。The ball 12 includes the second inner ring 11A, the first
The balls 12 are arranged between the races 11a, 11a of the inner race 11B and the races 10b, 10c of the outer race 10, respectively, and the balls 12 are held by the cages 13, 13 for each row.
Each of the retainers 13, 13 is designed to facilitate assembly.
It is preferable to have a pocket having such a size that the ball 12 does not fall off when the ball 12 is assembled in a single state.
【００１７】上記構成によれば、上記外輪１０の軌道部
１０b ,１０b と第２内輪１１Ａ,第１内輪１１Ｂの各軌
道部１１ａ,１１ａとの間に保持器１３,１３で保持した
玉１２を配置して、仮組みする。そして、各内輪１１
Ａ,１１Ｂの嵌合部１１ｃ,１１ｃを軸部材１４に軸方向
から隙間嵌めする。According to the above configuration, the ball 12 held by the retainers 13, 13 is provided between the raceways 10b, 10b of the outer race 10 and the raceways 11a, 11a of the second inner race 11A and the first inner race 11B. Place and temporarily assemble. And each inner ring 11
The fitting portions 11c, 11c of A, 11B are clearance-fitted to the shaft member 14 from the axial direction.
【００１８】このとき、上記第２内輪１１Ａの湾曲肩部
１１b に重量が一定の円筒形の重錘１６を乗せ、この重
錘１６の重量により、第２内輪１１Ａ、玉１２、外輪１
０、玉１２を経由して上記第１内輪１１Ｂを押圧し、第
１内輪１１Ｂの湾曲肩部１１ｂが軸部材１４のツバ部１
４ｂに当接するまで隙間嵌めする。この隙間嵌めは、重
量が一定の重錘１６で行うから、油圧装置で予圧を加え
る従来例と異なり、常に適正な予圧を設定できるように
なる。At this time, a cylindrical weight 16 having a constant weight is placed on the curved shoulder 11b of the second inner ring 11A, and the weight of the weight 16 causes the second inner ring 11A, the ball 12, and the outer ring 1 to move.
0, the first inner race 11B is pressed via the ball 12 and the curved shoulder 11b of the first inner race 11B is
4b until it abuts against 4b. Since this clearance fitting is performed by the weight 16 having a constant weight, an appropriate preload can always be set, unlike the conventional example in which a preload is applied by a hydraulic device.
【００１９】この隙間嵌めが完了すると、上記第２内輪
１１Ａの湾曲肩部１１ｂと軸部材１４との間の隙間に接
着剤１７を充填する。この接着剤１７で第２内輪１１Ａ
の嵌め外れが防止され、第１内輪１１Ｂは軸部材１４の
ツバ部１４ｂで嵌め外れが防止される。When this gap fitting is completed, the gap between the curved shoulder 11b of the second inner race 11A and the shaft member 14 is filled with an adhesive 17. With this adhesive 17, the second inner ring 11A
Of the first inner race 11B is prevented by the flange 14b of the shaft member 14.
【００２０】上記外輪１０及び各内輪１１Ａ,１１Ｂ
は、プレスやローリング等の安価な加工で製造できるか
ら、コスト安になる一方、素材が比較的薄肉で加工でき
るから、一般の軸受と比較して大きい玉１２を使用で
き、耐久性が向上する。The outer ring 10 and each inner ring 11A, 11B
Can be manufactured by inexpensive processing such as pressing and rolling, so that the cost can be reduced. On the other hand, since the material can be processed with a relatively thin wall, a ball 12 larger than a general bearing can be used, and the durability is improved. .
【００２１】また、外輪１０は、フランジ１０ｄと、環
状凹部１０ｅに接着剤を充填することにより、取付け機
能を有するから、取付け用部品が削減でき、コスト安に
なると共に、取付け用スペースも少なくてすむ。The outer ring 10 has a mounting function by filling the flange 10d and the annular recess 10e with an adhesive, so that the number of mounting parts can be reduced, the cost can be reduced, and the mounting space can be reduced. Yes.
【００２２】さらに、各内輪１１Ａ,１１Ｂの各湾曲肩
部１１ｂ,１１ｂは、軸部材１４に接触しないフリー状
態の部分１１e を有するから、衝撃が付加されたとき、
この部分１１e の弾性変形によって適度に衝撃を吸収す
るので、耐衝撃性が向上する。Further, since each of the curved shoulders 11b, 11b of each of the inner races 11A, 11B has a free portion 11e which does not come into contact with the shaft member 14, when an impact is applied,
Since the impact is appropriately absorbed by the elastic deformation of the portion 11e, the impact resistance is improved.
【００２３】さらにまた、上記各内輪１１Ａ,１１Ｂの
各湾曲肩部１１ｂ,１１ｂの外端部を、上記外輪１０の
内周面の軌道部１０c ,１０b の軌道端付近まで湾曲さ
せているから、上記湾曲肩部１１b の外端部と上記軌道
部１０c の端部とが形成するラビリンス構造により、軸
受内部のグリースの流出を防止できる。Further, the outer ends of the curved shoulders 11b, 11b of the inner races 11A, 11B are curved to the vicinity of the race ends of the races 10c, 10b on the inner peripheral surface of the outer race 10. Due to the labyrinth structure formed by the outer end of the curved shoulder 11b and the end of the track 10c, it is possible to prevent grease from flowing out of the bearing.
【００２４】上記実施例では内外輪１１Ａ，１１Ｂ，１
０をステンレス鋼製のものを用いているが、他の鋼、例
えば軸受鋼や銅系の合金の使用も可能である。In the above embodiment, the inner and outer rings 11A, 11B, 1
Although 0 is made of stainless steel, other steels such as bearing steel and copper-based alloys can be used.
【００２５】[0025]
【考案の効果】以上の説明からも明らかなように、本考
案の複列アンギュラコンタクト玉軸受装置は、第２内輪
が、軸部材に対して隙間嵌めして取り付けられると共
に、この第２内輪の湾曲肩部に重錘等を載せて、外輪と
第１,第２内輪との間の玉に予圧付与した後に、上記第
２内輪を軸部材に接着固定するものである。したがっ
て、従来例のように油圧装置で予圧を与える場合と異な
り、たとえば重量が一定の重錘で常に適性な予圧を設定
できるようになり、軸受装置の品質を安定させることが
できる。As is apparent from the above description, in the double row angular contact ball bearing device of the present invention, the second inner ring is mounted with a clearance fitted to the shaft member, and the second inner ring is mounted on the shaft member. A weight or the like is placed on the curved shoulder, and a preload is applied to a ball between the outer ring and the first and second inner rings, and then the second inner ring is bonded and fixed to a shaft member. Therefore, unlike the case where the preload is applied by the hydraulic device as in the conventional example, for example, an appropriate preload can always be set with a weight having a constant weight, and the quality of the bearing device can be stabilized.
【図１】 本考案の軸受装置の実施例の断面図である。FIG. 1 is a sectional view of an embodiment of the bearing device of the present invention.
【図２】 従来の軸受装置の断面図である。FIG. 2 is a sectional view of a conventional bearing device.
１０…外輪、１０ａ…環状凸部、１０ｂ,１０ｃ…軌道
部、１１Ａ…第２内輪,１１Ｂ…第１内輪、１１ａ…軌
道部、１１ｃ…嵌合部、１２…玉、１３…保持器、１４
…軸部材、１６…重錘、１７…接着剤。DESCRIPTION OF SYMBOLS 10 ... Outer ring, 10a ... Annular convex part, 10b, 10c ... Track part, 11A ... Second inner ring, 11B ... First inner ring, 11a ... Track part, 11c ... Fitting part, 12 ... Ball, 13 ... Cage, 14
... shaft member, 16 ... weight, 17 ... adhesive.
Claims (1)
側へ突出する環状凸部を有し、この環状凸部の両側の上
記内周面に軌道部を有するプレス板製の外輪と、 上記外輪の一方の軌道部の径方向内側に配置され、軸方
向外側外周に、軌道部を形成する湾曲肩部を有し、内周
面に軸部材に嵌合される嵌合部を有するプレス板製の第
１内輪と、 上記外輪の他方の軌道部の径方向内側に配置され、軸方
向外側外周に、軌道部を形成する湾曲肩部を有し、内周
面に軸部材に隙間嵌めされる嵌合部を有するプレス板製
の第２内輪と、 上記各内輪の各軌道部と上記外輪の各軌道部との間に配
置される複数の玉と、 上記各玉を列毎に保持する保持器とを備え、 上記第２内輪は、上記軸部材に対して隙間嵌めして取り
付けられ、軸方向に予圧付与した後に上記軸部材に接着
固定されていることを特徴とする複列アンギュラコンタ
クト玉軸受装置。1. A press plate made of a press plate having an annular convex portion protruding radially inward at a substantially intermediate portion in the axial direction of the inner peripheral surface, and having a track portion on the inner peripheral surface on both sides of the annular convex portion. An outer ring, a fitting portion disposed radially inward of one of the races of the outer race, having a curved shoulder on the outer periphery in the axial direction to form the race, and being fitted to the shaft member on the inner peripheral surface; A first inner ring made of a press plate having: a radially inner side of the other raceway portion of the outer race, a curved shoulder portion forming a raceway portion on an outer periphery in an axial direction, and a shaft member on an inner peripheral surface. A second inner ring made of a press plate having a fitting portion to be gap-fitted into the inner ring; a plurality of balls arranged between each of the races of the inner ring and the respective races of the outer ring; And a retainer for holding the second inner ring. The second inner ring is attached to the shaft member by a clearance fit, and is provided with a preload in the axial direction. Double row angular contact ball bearing apparatus characterized by being adhesively fixed to the shaft member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4157092U JP2563692Y2 (en) | 1992-06-17 | 1992-06-17 | Double row angular contact ball bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4157092U JP2563692Y2 (en) | 1992-06-17 | 1992-06-17 | Double row angular contact ball bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH061835U JPH061835U (en) | 1994-01-14 |
| JP2563692Y2 true JP2563692Y2 (en) | 1998-02-25 |
Family
ID=12612106
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4157092U Expired - Fee Related JP2563692Y2 (en) | 1992-06-17 | 1992-06-17 | Double row angular contact ball bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2563692Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8047722B2 (en) | 2006-11-07 | 2011-11-01 | Ntn Corporation | Wheel bearing apparatus for a vehicle |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007321776A (en) * | 2006-05-30 | 2007-12-13 | Jtekt Corp | Rolling bearing device for wheel |
| WO2008056446A1 (en) * | 2006-11-07 | 2008-05-15 | Ntn Corporation | Bearing device for wheel |
| JP4205752B2 (en) * | 2006-11-07 | 2009-01-07 | Ｎｔｎ株式会社 | Wheel bearing device |
| JP2007278518A (en) * | 2007-07-06 | 2007-10-25 | Jtekt Corp | Bearing device for vehicle |
| JP2009162270A (en) * | 2007-12-28 | 2009-07-23 | Ntn Corp | Bearing device for wheel and method of manufacturing inner ring of bearing |
| JP2009144859A (en) * | 2007-12-17 | 2009-07-02 | Ntn Corp | Bearing device for wheel and method for manufacturing outer ring |
| JP2009197901A (en) * | 2008-02-21 | 2009-09-03 | Ntn Corp | Wheel bearing device |
| JP2009197899A (en) * | 2008-02-21 | 2009-09-03 | Ntn Corp | Double-row angular bearing |
| WO2009078337A1 (en) | 2007-12-17 | 2009-06-25 | Ntn Corporation | Double-row angular bearing, bearing device for wheel, method of producing outer ring, and method of producing inner ring |
| JP6209374B2 (en) * | 2013-07-05 | 2017-10-04 | セイコーインスツル株式会社 | Bearing device, bearing device manufacturing method, and information recording / reproducing device |
-
1992
- 1992-06-17 JP JP4157092U patent/JP2563692Y2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8047722B2 (en) | 2006-11-07 | 2011-11-01 | Ntn Corporation | Wheel bearing apparatus for a vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH061835U (en) | 1994-01-14 |
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