JP5803234B2 - Tandem angular contact ball bearings - Google Patents

Tandem angular contact ball bearings Download PDF

Info

Publication number
JP5803234B2
JP5803234B2 JP2011092584A JP2011092584A JP5803234B2 JP 5803234 B2 JP5803234 B2 JP 5803234B2 JP 2011092584 A JP2011092584 A JP 2011092584A JP 2011092584 A JP2011092584 A JP 2011092584A JP 5803234 B2 JP5803234 B2 JP 5803234B2
Authority
JP
Japan
Prior art keywords
diameter
balls
peripheral surface
small
outer 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.)
Active
Application number
JP2011092584A
Other languages
Japanese (ja)
Other versions
JP2011241978A (en
Inventor
孝道 田中
孝道 田中
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP2011092584A priority Critical patent/JP5803234B2/en
Publication of JP2011241978A publication Critical patent/JP2011241978A/en
Application granted granted Critical
Publication of JP5803234B2 publication Critical patent/JP5803234B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F16C19/02—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
    • F16C19/182—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 in tandem 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
    • F16C33/38—Ball cages
    • F16C33/40—Ball cages for multiple rows of balls
    • F16C33/405—Ball cages for multiple rows of balls with two or more juxtaposed cages joined together or interacting with each other
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Description

この発明は、自動車用のデファレンシャルギヤ、トランスファ、変速機（手動変速機、自動変速機を含む）等の回転機械装置に組み込まれて、ラジアル荷重及びスラスト荷重が加わった状態で回転する回転軸を支承する為のタンデムアンギュラ型玉軸受の改良に関する。具体的には、ピッチ円直径の大きな大径列側の玉を配置した部分に過剰な潤滑油が送り込まれる事を防止して、運転時の回転抵抗（動トルク）を低く抑えられる構造の実現を図るものである。   The present invention relates to a rotating shaft that is incorporated in a rotary machine device such as a differential gear, a transfer, and a transmission (including a manual transmission and an automatic transmission) for an automobile and that rotates in a state where a radial load and a thrust load are applied. The present invention relates to an improvement of a tandem angular contact ball bearing for supporting. Specifically, it is possible to prevent excessive lubrication oil from being sent to the part where the balls on the large-diameter row with a large pitch circle diameter are placed, and to realize a structure that can keep the rotational resistance (dynamic torque) during operation low Is intended.

例えば自動車用のデファレンシャルギヤを構成する為のピニオン軸はデファレンシャルケース内に、複数個の転がり軸受により回転自在に支持する。デファレンシャルギヤの運転時に前記ピニオン軸には、大きなラジアル荷重及びスラスト荷重が同時に加わる為、このピニオン軸を支持する為の軸受として、ラジアル、スラスト両方向の負荷容量が十分に大きなものを使用する必要がある。又、近年に於ける自動車の省燃費化の流れにより、デファレンシャルケースに対してピニオン軸を支持する為の転がり軸受として、ラジアル、スラスト両方向に関する大きな荷重を支承可能で、しかも円すいころ軸受に比べて動トルクを低く抑えられる、タンデムアンギュラ型玉軸受を使用する事が、特許文献１〜５に記載されている様に、従来から考えられている。   For example, a pinion shaft for constituting a differential gear for automobiles is rotatably supported by a plurality of rolling bearings in a differential case. Since large radial load and thrust load are simultaneously applied to the pinion shaft during differential gear operation, it is necessary to use a bearing with sufficient load capacity in both radial and thrust directions to support the pinion shaft. is there. In addition, due to the recent trend of reducing fuel consumption in automobiles, it is possible to support large loads in both radial and thrust directions as rolling bearings for supporting the pinion shaft with respect to the differential case, and compared to tapered roller bearings. As described in Patent Documents 1 to 5, it has been conventionally considered to use a tandem angular ball bearing that can keep the dynamic torque low.

図７は、特許文献１に記載された、タンデムアンギュラ型玉軸受により構成した、デファレンシャルギヤ用ピニオン軸の回転支持装置を示している。尚、デファレンシャルギヤ全体の構造及び作用は従来から周知であるし、特許文献１〜３にも記載されている為、詳しい説明を省略し、以下、前記回転支持装置部分の構造に就いて説明する。デファレンシャルケースの内部に１対の玉軸受１、２を、互いに離隔した状態で配置し、これら両玉軸受１、２によりピニオン軸３を支持している。これら両玉軸受１、２は、それぞれ玉に接触角を持たせたアンギュラ型玉軸受であり、これら両玉軸受１、２の接触角の方向を互いに逆向きとしている。従って、前記ピニオン軸３は、前記デファレンシャルケースの内部に、ラジアル荷重だけでなく、両方向のスラスト荷重を支承される状態で、回転自在に支持されている。   FIG. 7 shows a rotational support device for a pinion shaft for a differential gear, which is configured by a tandem angular ball bearing described in Patent Document 1. The structure and operation of the entire differential gear are well known and described in Patent Documents 1 to 3. Therefore, detailed description is omitted, and the structure of the rotation support device portion will be described below. . A pair of ball bearings 1 and 2 are arranged inside the differential case in a state of being separated from each other, and the pinion shaft 3 is supported by these ball bearings 1 and 2. These ball bearings 1 and 2 are angular ball bearings in which the balls have contact angles, and the contact angles of these ball bearings 1 and 2 are opposite to each other. Therefore, the pinion shaft 3 is rotatably supported in the differential case in a state where not only a radial load but also a thrust load in both directions is supported.

又、前記両玉軸受１、２のうち、比較的大きなラジアル荷重及びスラスト荷重を支承するピニオンギヤ４側（図７の右側）の玉軸受１として、本発明の対象となる、タンデムアンギュラ型玉軸受を使用している。これに対して、比較的小さなラジアル荷重及びスラスト荷重しか支承しない反ピニオンギヤ４側（図７の左側）の玉軸受２は、単列アンギュラ型の玉軸受を使用している。但し、ピニオンギヤ側だけでなく、反ピニオンギヤ側の玉軸受もタンデムアンギュラ型とする構造も、特許文献１〜３に記載されており、従来から知られている。この様な構造の場合、反ピニオンギヤ側の玉軸受も、本発明の対象となる。何れにしても、前記ピニオンギヤ４側の玉軸受１は、ラジアル荷重に加えて、このピニオンギヤ４と噛合したリングギヤ（図示省略）から離れる方向（図７の左向き）のスラスト荷重を支承する。これに対して反ピニオンギヤ４側の玉軸受２は、ラジアル荷重に加えて、前記リングギヤに近付く方向（図７の右向き）のスラスト荷重を支承する。   Of the two ball bearings 1 and 2, the tandem angular ball bearing, which is the object of the present invention, is used as the ball bearing 1 on the pinion gear 4 side (the right side in FIG. 7) that supports a relatively large radial load and thrust load. Is used. On the other hand, the ball bearing 2 on the anti-pinion gear 4 side (left side in FIG. 7) that supports only a relatively small radial load and thrust load uses a single-row angular ball bearing. However, a structure in which not only the pinion gear side but also the ball bearing on the anti-pinion gear side is a tandem angular type is described in Patent Documents 1 to 3, and is conventionally known. In the case of such a structure, the ball bearing on the anti-pinion gear side is also an object of the present invention. In any case, in addition to the radial load, the ball bearing 1 on the pinion gear 4 side supports a thrust load in a direction away from the ring gear (not shown) meshed with the pinion gear 4 (leftward in FIG. 7). On the other hand, the ball bearing 2 on the anti-pinion gear 4 side supports a thrust load in a direction approaching the ring gear (rightward in FIG. 7) in addition to the radial load.

本例の場合、タンデムアンギュラ型玉軸受である、前記ピニオンギヤ４側の玉軸受１は、外輪５と、内輪６と、複数個の玉７ａ、７ｂと、１対の保持器８ａ、８ｂとを備える。このうちの外輪５は、内周面に、互いに内径が異なる、複列アンギュラ型の外輪軌道９ａ、９ｂを設けている。これら両外輪軌道９ａ、９ｂの内径は、前記ピニオンギヤ４側の外輪軌道９ａの方が大きく、このピニオンギヤ４と反対側の外輪軌道９ｂの方が小さい。又、前記内輪６は、前記外輪５の内径側にこの外輪５と同心に配置されたもので、外周面のうちで前記両外輪軌道９ａ、９ｂに対向する部分に、互いに外径が異なる、複列アンギュラ型の内輪軌道１０ａ、１０ｂを設けている。これら両内輪軌道１０ａ、１０ｂの外径は、前記ピニオンギヤ４側の内輪軌道１０ａの方が大きく、このピニオンギヤ４と反対側の外輪軌道１０ｂの方が小さい。又、前記各玉７ａ、７ｂは、前記両外輪軌道９ａ、９ｂと前記両内輪軌道１０ａ、１０ｂとの間に、それぞれの列毎に複数個ずつ、両列で同じ方向の（並列組み合わせ型の）接触角を付与された状態で、転動自在に設けられている。更に、前記両保持器８ａ、８ｂは、互いに直径が異なり、それぞれが前記両列の玉７ａ、７ｂを、転動自在に保持している。尚、これら両列の玉７ａ、７ｂの直径は、互いに同じ場合も、或いは、互いに異なる場合もある。   In the case of this example, the ball bearing 1 on the pinion gear 4 side, which is a tandem angular ball bearing, includes an outer ring 5, an inner ring 6, a plurality of balls 7a and 7b, and a pair of cages 8a and 8b. Prepare. Of these, the outer ring 5 is provided with double-row angular outer ring raceways 9a and 9b having different inner diameters on the inner peripheral surface. The inner diameters of these outer ring raceways 9 a and 9 b are larger in the outer ring raceway 9 a on the pinion gear 4 side and smaller in the outer ring raceway 9 b on the opposite side to the pinion gear 4. Further, the inner ring 6 is disposed concentrically with the outer ring 5 on the inner diameter side of the outer ring 5, and the outer diameters of the outer peripheral surfaces of the inner ring 6 are opposite to the outer ring raceways 9a and 9b. Double row angular type inner ring raceways 10a and 10b are provided. The outer diameters of both the inner ring raceways 10a and 10b are larger in the inner ring raceway 10a on the pinion gear 4 side and smaller in the outer ring raceway 10b on the opposite side to the pinion gear 4. Further, a plurality of balls 7a, 7b are arranged in the same direction in both rows (parallel combination type) between the outer ring raceways 9a, 9b and the inner ring raceways 10a, 10b. ) It is provided so as to be able to roll while being given a contact angle. Furthermore, both the cages 8a and 8b have different diameters, and each retains the balls 7a and 7b in both rows in a freely rollable manner. The diameters of the balls 7a and 7b in both rows may be the same or different from each other.

上述の様なタンデムアンギュラ型の玉軸受１は、運転時に円すいころ軸受の場合の様な大きな滑り接触を伴わないので、動トルクを低く抑えられ、デファレンシャルギヤの抵抗を低くできる。又、複列に配置した玉７ａ、７ｂにより、前記ピニオンギヤ４と前記リングギヤとの噛合部で発生するラジアル荷重及びスラスト荷重を支承する為、これら両方向の荷重に関する負荷容量も十分に確保できる。   Since the tandem angular ball bearing 1 as described above is not accompanied by a large sliding contact as in the case of a tapered roller bearing during operation, the dynamic torque can be kept low and the resistance of the differential gear can be reduced. Further, since the balls 7a and 7b arranged in a double row support the radial load and the thrust load generated at the meshing portion of the pinion gear 4 and the ring gear, it is possible to sufficiently secure the load capacity related to the loads in both directions.

上述の様なタンデムアンギュラ型玉軸受を組み込んだデファレンシャルギヤの性能を向上させる為には、このタンデムアンギュラ型玉軸受の運転時の回転抵抗（動トルク）を低減させる事が重要である。動トルクが増大する要因は種々存在するが、前記各玉７ａ、７ｂの転動面と前記両外輪軌道９ａ、９ｂ及び前記両内輪軌道１０ａ、１０ｂとの転がり接触部を潤滑する為の潤滑油が過剰になる事も、要因の一つになる。周知の様にデファレンシャルギヤの潤滑は、デファレンシャルケースの底部に貯溜された潤滑油（デファレンシャルオイル）をリング歯車により掻き揚げて各可動部に送り込む様にしている。前記タンデムアンギュラ型の玉軸受１を潤滑する為の潤滑油は、前記外輪５の内周面と前記内輪６の外周面との間に存在して前記各玉７ａ、７ｂを設置した内部空間１１内に、この内部空間１１の端部開口から送り込まれる。例えばこの内部空間１１内に小径側（図７の左側）開口端部から送り込まれ、この内部空間１１内を、前記各玉７ａ、７ｂの公転運動に伴うポンプ作用等により、この内部空間１１の小径側から大径側に、図７の右方向に流れつつ、前記各転がり接触部を潤滑する。   In order to improve the performance of a differential gear incorporating a tandem angular ball bearing as described above, it is important to reduce the rotational resistance (dynamic torque) during operation of the tandem angular ball bearing. Although there are various factors that increase the dynamic torque, the lubricating oil for lubricating the rolling contact portions between the rolling surfaces of the balls 7a and 7b and the outer ring raceways 9a and 9b and the inner ring raceways 10a and 10b. One of the factors is that the amount of money is excessive. As is well known, in the differential gear lubrication, the lubricating oil (differential oil) stored at the bottom of the differential case is lifted by a ring gear and sent to each movable part. Lubricating oil for lubricating the tandem angular ball bearing 1 exists between the inner peripheral surface of the outer ring 5 and the outer peripheral surface of the inner ring 6, and an internal space 11 in which the balls 7a and 7b are installed. It is fed into from the end opening of the internal space 11. For example, it is fed into the internal space 11 from the small diameter side (left side in FIG. 7) opening end, and the internal space 11 is pumped by the revolving motion of the balls 7a and 7b. The respective rolling contact portions are lubricated while flowing in the right direction in FIG. 7 from the small diameter side to the large diameter side.

これら各転がり接触部の耐久性を確保する為に、前記内部空間１１内を流れる潤滑油の量を必要最低限確保する事は必要であるが、この内部空間１１内を流れる潤滑油の量が過剰になると、前記動トルクが徒に増大する。即ち、前記各転がり接触部に過剰な潤滑油が存在すると、前記各玉７ａ、７ｂの自転及び公転運動に伴って、これら各玉７ａ、７ｂが、これら各玉７ａ、７ｂの転動面や前記両外輪軌道９ａ、９ｂ、更には前記両内輪軌道１０ａ、１０ｂに付着した余分な潤滑油を押し退ける為に要する力（潤滑油の攪拌抵抗）が増大し、前記動トルクが増大する。勿論、前記内部空間１１内への潤滑油の送り込み量を適正に（過剰にならない様に）規制すれば良いが、前述した様に、前記内部空間１１内への潤滑油の送り込みは、リング歯車の回転に基づく単純な機構により図っている為、前記送り込み量を適正に規制する事は難しい。又、単に前記内部空間１１の開口部に絞り構造を設けたりした場合には、前記底部に貯溜された潤滑油の量が少ない場合等に、潤滑不良により、前記玉軸受１に焼き付等の故障が発生し易くなる為、好ましくない。   In order to ensure the durability of each rolling contact portion, it is necessary to secure the minimum amount of lubricating oil flowing in the internal space 11, but the amount of lubricating oil flowing in the internal space 11 is When it becomes excessive, the dynamic torque increases. That is, if excessive lubricating oil is present at each rolling contact portion, the balls 7a and 7b are caused to rotate and revolve along the rolling surfaces of the balls 7a and 7b. The force (stirring resistance of the lubricating oil) required to push away the excess lubricating oil adhering to both the outer ring raceways 9a and 9b and further the both inner ring raceways 10a and 10b increases, and the dynamic torque increases. Of course, the amount of lubricating oil fed into the internal space 11 may be regulated appropriately (so as not to be excessive). As described above, the lubricating oil is fed into the internal space 11 by a ring gear. Therefore, it is difficult to properly regulate the feeding amount. In addition, when a throttle structure is simply provided in the opening of the internal space 11, when the amount of lubricating oil stored in the bottom is small, the ball bearing 1 may be seized due to poor lubrication. This is not preferable because failure tends to occur.

この様な事情に鑑みて特許文献３には、図８に示す様に、内部空間１１の小径側開口端部と両列の各玉７ａ、７ｂ同士の間とに、それぞれ接触式のシールリング１２ａ、１２ｂを設け、これら両シールリング１２ａ、１２ｂ同士の間にグリースを封入する構造に関する発明が記載されている。この様な構造の場合、前記内部空間１１内を過剰な潤滑油が流通し、この潤滑油を前記各玉７ａ、７ｂが攪拌する事に伴う抵抗の増大は抑えられる。但し、前記両シールリング１２ａ、１２ｂのシールリップの先端縁と相手面（内輪６の外周面）との摺動抵抗が加わる為、玉軸受１ａ全体としての動トルクを十分に低くはできない。   In view of such circumstances, as shown in FIG. 8, Patent Document 3 discloses a contact-type seal ring between the small-diameter-side opening end of the internal space 11 and the balls 7a and 7b in both rows. An invention relating to a structure in which 12a and 12b are provided and grease is sealed between the seal rings 12a and 12b is described. In the case of such a structure, an increase in resistance caused by excessive lubricating oil flowing in the internal space 11 and stirring the lubricating oil by the balls 7a and 7b can be suppressed. However, since the sliding resistance between the tip edge of the seal lip of both the seal rings 12a and 12b and the mating surface (the outer peripheral surface of the inner ring 6) is added, the dynamic torque of the ball bearing 1a as a whole cannot be made sufficiently low.

更に、特許文献４、５には、図９に示す様に、小径側の保持器８ｂ′の端部に、径方向外方に突出した外向鍔部１３を設けた構造が記載されている。この外向鍔部１３は、内部空間１１内を潤滑油が流通する事に対する抵抗になり、この潤滑油の流通量を多少制限する機能を果たすものとは考えられるが、前記外向鍔部１３の外周縁と外輪５の内周面との間に大きな隙間が存在する為、前記流通量を十分には制限できないものと考えられる。即ち、前記内部空間１１内にその小径側開口から流入した潤滑油は、前記外向鍔部１３に付着した後、前記保持器８ｂ′の回転に伴う遠心力により前記外輪５の内周面に移動し、そのうちの大部分が、この外輪５の内周面に沿って、大径列側の玉７ａに関する転がり接触部に送り込まれる。従って、前記流通量の低減による、動トルクの低減は、殆ど期待できない。   Furthermore, Patent Documents 4 and 5 describe a structure in which an outward flange 13 protruding outward in the radial direction is provided at the end of the small diameter side cage 8b 'as shown in FIG. The outward flange 13 serves as a resistance against the flow of the lubricating oil in the internal space 11 and is considered to fulfill the function of restricting the flow amount of the lubricating oil to some extent. Since there is a large gap between the peripheral edge and the inner peripheral surface of the outer ring 5, it is considered that the flow rate cannot be sufficiently limited. That is, the lubricating oil that has flowed into the internal space 11 from the small-diameter side opening adheres to the outward flange 13 and then moves to the inner peripheral surface of the outer ring 5 due to the centrifugal force associated with the rotation of the cage 8b '. And most of them are sent along the inner peripheral surface of the outer ring 5 to the rolling contact portion related to the balls 7a on the large diameter row side. Therefore, the reduction of the dynamic torque due to the reduction of the circulation amount is hardly expected.

特開２００４−１６９８９０号公報JP 2004-169890 A 特開２００４−２４５２３１号公報JP 2004-245231 A 特開２００７−２６３２６６号公報JP 2007-263266 A 特開２００８−１３８８４１号公報JP 2008-138841 A 特開２００９−３６３４８号公報JP 2009-36348 A

本発明は、上述の様な事情に鑑み、ピッチ円直径の大きな大径列側の玉を配置した部分に過剰な潤滑油が送り込まれる事を防止して、運転時の回転抵抗（動トルク）を低く抑えられる構造を実現すべく発明したものである。   In view of the circumstances as described above, the present invention prevents excessive lubricating oil from being fed into the portion where the ball on the large diameter row having a large pitch circle diameter is arranged, and rotational resistance (dynamic torque) during operation. The invention was invented to realize a structure that can keep the above low.

本発明のタンデムアンギュラ型玉軸受は、特許文献１〜５に記載される等により従来から知られているタンデムアンギュラ型玉軸受と同様に、外輪と、内輪と、複数個の玉と、１対の保持器とを備える。
このうちの外輪は、それぞれがアンギュラ型であって内径が互いに異なる２列の外輪軌道を内周面に、互いに同じ向きに設けている。
又、前記内輪は、それぞれがアンギュラ型であって外径が互いに異なる２列の内輪軌道を外周面に、互いに同じ向きに設けたもので、前記外輪の内径側にこの外輪と同心に配置している。
又、前記各玉は、前記両外輪軌道と前記両内輪軌道との間に、それぞれの列毎に複数個ずつ、両列同士の間で同じ方向の接触角を付与され、且つ、ピッチ円直径を互いに異ならせた状態で、転動自在に設けている。
更に、前記両保持器は、両列毎に互いに独立して直径が互いに異なるもので、前記各玉を転動自在に保持している。 The tandem angular ball bearing according to the present invention includes an outer ring, an inner ring, a plurality of balls, and a pair, as in the case of tandem angular ball bearings conventionally known as described in Patent Documents 1 to 5. And a cage.
Of these, the outer ring is an angular type and has two rows of outer ring raceways having different inner diameters on the inner peripheral surface in the same direction.
The inner ring is an angular type and has two rows of inner ring raceways with different outer diameters provided on the outer peripheral surface in the same direction, and is arranged concentrically with the outer ring on the inner diameter side of the outer ring. ing.
Each of the balls is provided with a contact angle in the same direction between the outer ring raceways and the inner ring raceways in a same direction between the rows, and a plurality of pitch circle diameters. Are provided so that they can roll freely.
Further, the two cages are different from each other in diameter in each row, and hold the balls so that they can roll.

特に、本発明のタンデムアンギュラ型玉軸受に於いては、前記ピッチ円直径が大きい大径列側の玉を転動自在に保持する為の大径側保持器を構成する円環状の大径側リム部を、前記ピッチ円直径が小さい小径列側の玉に対向する部分に設けている。又、追加的に、この小径列側の玉を転動自在に保持する為の小径側保持器を構成する円環状の小径側リム部を、前記大径側リム部の径方向内側に配置している。そして、この大径側リム部を、この小径列側の玉を配置した部分から、前記大径列側の玉を配置した部分に向かう潤滑油の一部を、この小径列側に戻す形状を有するものとしている。具体的には、前記大径側リム部の内周面を全周に亙り、小径列側の玉に近づくほど内径が大きくなる方向に傾斜させる事で、この小径列側の玉を配置した部分から前記大径列側の玉を配置した部分に向かう潤滑油の一部を、この小径列側に戻すものとしている。
尚、前記大径側リム部の形状としては、本発明の技術的範囲から外れるものの、次の様な形状を採用する事も考えられる。即ち、大径側リム部を、大径列側の玉を転動自在に保持する為のポケットを設けた本体部分よりも径方向に関する幅寸法が大きくなったフランジ状とする。そして、このフランジ状の大径側リム部の外周縁と外輪の内周面との距離を、前記本体部分とこの内周面との距離よりも短くする。 In particular, in the tandem angular contact ball bearing of the present invention, an annular large-diameter side that constitutes a large-diameter side retainer for holding the balls on the large-diameter row side having a large pitch circle diameter so as to roll freely. A rim portion is provided at a portion facing the ball on the small diameter row side where the pitch circle diameter is small. In addition, an annular small-diameter side rim portion that constitutes a small-diameter side retainer for holding the balls on the small-diameter row side in a rollable manner is disposed radially inside the large-diameter side rim portion. ing. And the shape which returns this large diameter side rim part to this small diameter row side a part of lubricating oil which goes to the portion which arranged the ball on the large diameter row side from the portion which arranged the ball on the small diameter row side I have it. Specifically, the portion on which the balls on the small diameter row side are arranged by inclining the inner peripheral surface of the large diameter side rim portion over the entire circumference and inclining in a direction in which the inner diameter increases as it approaches the ball on the small diameter row side A part of the lubricating oil going to the portion where the balls on the large diameter row side are arranged is returned to the small diameter row side.
In addition, as a shape of the said large diameter side rim | limb part, although it remove | deviates from the technical scope of this invention, it is also considered to employ | adopt the following shapes. That is, the large-diameter side rim portion is formed into a flange shape having a larger width dimension in the radial direction than the main body portion provided with a pocket for holding the balls on the large-diameter row side so as to roll. Then, the distance between the outer peripheral edge of the flange-shaped large-diameter side rim portion and the inner peripheral surface of the outer ring is made shorter than the distance between the main body portion and the inner peripheral surface.

この様な本発明を実施する場合に好ましくは、請求項２に記載した発明の様に、追加的に、前記大径側リム部の外周面を、前記外輪の内周面に全周に亙り近接対向させる。 In the case of carrying out the present invention as described above, preferably, as in the invention described in claim 2, the outer peripheral surface of the large-diameter side rim portion is additionally provided over the entire inner peripheral surface of the outer ring. Adjacent to each other.

或いは、請求項３に記載した発明の様に、追加的に、前記小径側リム部の外周面を、径方向外方に向かうほど、前記小径側保持器の軸方向中央部に向かう方向に傾斜させる。又、前記小径側リム部の外周面と前記大径側リム部の内周面とを、径方向及び軸方向に重畳する状態で互いに対向させる。 Alternatively, as in the invention described in claim 3, in addition, the outer peripheral surface of the small-diameter side rim portion is inclined in the direction toward the axial central portion of the small-diameter side cage as it goes radially outward. Let Further, the outer peripheral surface of the small-diameter side rim portion and the inner peripheral surface of the large-diameter side rim portion are opposed to each other in a state where they overlap in the radial direction and the axial direction.

上述の様に構成する本発明のタンデムアンギュラ型玉軸受の場合には、大径側保持器を構成する大径側リム部が、小径列側の玉部分から大径列側の玉部分に向かう潤滑油の一部を、この小径列側に戻す。この為、ピッチ円直径の大きな大径列側の玉を配置した部分に過剰な潤滑油が送り込まれる事を防止して、運転時の回転抵抗（動トルク）を低く抑えられる。即ち、ピッチ円直径の小さな小径列側の玉に比べて周速（自転速度及び公転速度）が大きな、前記大径列側の玉を配置した部分に存在する潤滑油の量を適正にして、前記動トルクの低減を図れる。   In the case of the tandem angular ball bearing of the present invention configured as described above, the large-diameter side rim portion constituting the large-diameter side cage is directed from the ball portion on the small-diameter row side to the ball portion on the large-diameter row side. A part of the lubricating oil is returned to the small diameter row side. For this reason, it is possible to prevent excessive lubricating oil from being fed into the portion where the balls on the large diameter row with a large pitch circle diameter are arranged, and to keep the rotational resistance (dynamic torque) during operation low. That is, the circumferential speed (spinning speed and revolution speed) is larger than the small diameter row side ball having a small pitch circle diameter, and the amount of lubricating oil present in the portion where the large diameter row side ball is arranged is made appropriate, The dynamic torque can be reduced.

本発明の実施の形態の第１例を示す部分断面図。The fragmentary sectional view which shows the 1st example of embodiment of this invention. 同第２例を示す部分断面図。The fragmentary sectional view which shows the 2nd example. 同第３例を示す部分断面図。The fragmentary sectional view which shows the 3rd example. 同第４例を示す部分断面図。The fragmentary sectional view which shows the 4th example. 本発明に関する参考例を示す部分断面図。 The fragmentary sectional view which shows the reference example regarding this invention . 本発明の実施の形態の第５例を示す部分断面図。 The fragmentary sectional view which shows the 5th example of embodiment of this invention . 従来構造の第１例のタンデムアンギュラ型玉軸受を組み込んだデファレンシャルギヤの１例を示す断面図。Sectional drawing which shows an example of the differential gear incorporating the tandem angular ball bearing of the 1st example of the conventional structure. 従来構造の第２例のタンデムアンギュラ型玉軸受を組み込んだデファレンシャルギヤの一部を示す部分断面図。The fragmentary sectional view which shows a part of differential gear incorporating the tandem angular ball bearing of the 2nd example of the conventional structure. 同第３例のタンデムアンギュラ型玉軸受の半部断面図。The half part sectional view of the tandem angular contact type ball bearing of the 3rd example.

［実施の形態の第１例］
図１は、請求項１、２に対応する、本発明の実施の形態の第１例を示している。本例のタンデムアンギュラ型の玉軸受１ｃは、図７〜９により先に説明した従来から知られているタンデムアンギュラ型の玉軸受１、１ａ、１ｂと同様に、外輪５と、内輪６と、複数個の玉７ａ、７ｂと、１対の保持器１４、１５とを備える。
このうちの外輪５は内周面に、それぞれがアンギュラ型であって内径が互いに異なる２列の外輪軌道９ａ、９ｂを、互いに同じ向きに設けている。
又、前記内輪６は外周面に、それぞれがアンギュラ型であって外径が互いに異なる２列の内輪軌道１０ａ、１０ｂを、互いに同じ向きに設けている。この様な内輪６は前記外輪５の内径側に、この外輪５と同心に配置している。
又、前記各玉７ａ、７ｂは、前記両外輪軌道９ａ、９ｂと前記両内輪軌道１０ａ、１０ｂとの間に、それぞれの列毎に複数個ずつ、両列同士の間で同じ方向の接触角を付与し、且つ、ピッチ円直径を互いに異ならせた状態で、転動自在に設けている。
更に、前記両保持器１４、１５は、両列毎に互いに独立して直径が互いに異なるもので、前記各玉７ａ、７ｂを転動自在に保持している。
以上の構成に就いては、前述した各従来構造の場合と同様である。 [First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention corresponding to claims 1 and 2. The tandem angular ball bearing 1c of this example is similar to the conventionally known tandem angular ball bearings 1, 1a, 1b described above with reference to FIGS. A plurality of balls 7 a and 7 b and a pair of cages 14 and 15 are provided.
Of these, the outer ring 5 is provided with two rows of outer ring raceways 9a, 9b in the same direction on the inner peripheral surface, each of which is angular and has different inner diameters.
Further, the inner ring 6 is provided with two rows of inner ring raceways 10a and 10b in the same direction on the outer peripheral surface, each of which is angular and has different outer diameters. Such an inner ring 6 is arranged concentrically with the outer ring 5 on the inner diameter side of the outer ring 5.
The balls 7a and 7b have a plurality of contact angles in the same direction between the outer ring raceways 9a and 9b and the inner ring raceways 10a and 10b. And is provided so as to be able to roll in a state where the pitch circle diameters are different from each other.
Further, the two cages 14 and 15 are different from each other in diameter in each row, and hold the balls 7a and 7b so as to roll freely.
About the above structure, it is the same as that of the case of each conventional structure mentioned above.

特に、本例のタンデムアンギュラ型の玉軸受１ｃの場合には、前記両保持器１４、１５の構造を組み合わせる事により、これら両保持器１４、１５及び前記各玉７ａ、７ｂを設置した内部空間１１内を流通する潤滑油の量、特に、ピッチ円直径が大きな、大径列側の前記各玉７ａの設置部分に送り込まれる潤滑油の量が過剰になる事を防止している。以下、この点に就いて説明する。
前記両保持器１４、１５は、何れも軸方向両端部にそれぞれが円環状であるリム部を設けると共に、軸方向中間部の複数個所に、それぞれの内側に前記各玉７ａ、７ｂを転動自在に保持する為のポケットを、円周方向に関して等間隔に設けている。 In particular, in the case of the tandem angular ball bearing 1c of this example, by combining the structures of the two retainers 14 and 15, the internal space in which the retainers 14 and 15 and the balls 7a and 7b are installed. The amount of the lubricating oil flowing through the inside 11, in particular, the amount of the lubricating oil sent to the installation portion of the balls 7 a on the large diameter row side having a large pitch circle diameter is prevented from becoming excessive. Hereinafter, this point will be described.
Each of the cages 14 and 15 is provided with rim portions each having an annular shape at both ends in the axial direction, and the balls 7a and 7b are rolled inside a plurality of portions in the axially intermediate portion. Pockets for holding freely are provided at equal intervals in the circumferential direction.

本例の場合には、前記両保持器１４、１５を構成する、それぞれ１対ずつのリム部のうち、前記大径列側の前記各玉７ａと、ピッチ円直径が小さな小径列側の前記各玉７ｂとの間部分に配置されるリム部１６、１７の形状、及び、これら両リム部１６、１７同士の組み合わせ状態を工夫している。
具体的には、前記大径列側の各玉７ａを保持する、特許請求の範囲に記載した大径側保持器である保持器１４を構成する、前記リム部１６の径方向内側に、前記小径列側の各玉７ｂを保持する、特許請求の範囲に記載した小径側保持器である保持器１５を構成する、前記リム部１７を配置している。 In the case of this example, among the pair of rim portions constituting the cages 14 and 15, the balls 7a on the large diameter row side and the small diameter row side on the small diameter row side with a small pitch circle diameter. The shape of the rim | limb parts 16 and 17 arrange | positioned between each ball | bowl 7b, and the combined state of both these rim | limb parts 16 and 17 are devised.
Specifically, on the radially inner side of the rim portion 16 constituting the retainer 14 that is a large-diameter side retainer described in the claims that retains each ball 7a on the large-diameter row side, The said rim | limb part 17 which comprises the holder | retainer 15 which hold | maintains each ball 7b of the small diameter row | line | column side and is a small diameter side holder described in the claim is arrange | positioned.

又、前記大径列側のリム部１６の内周面に、前記小径列側の玉７ｂに近づくほど内径が大きくなる方向に傾斜した傾斜面部１８を全周に亙り形成している。本例の場合には、この傾斜面部１８を、内径側の急傾斜面部と外径側の緩傾斜面部とを組み合わせたものとしている。尚、図示の例では、これら急傾斜面部と緩傾斜面部との間に、円筒面部を設けている。このうちの急傾斜面部は勿論、緩傾斜面部に関しても、前記小径列側の玉７ｂに近づくほど内径が大きくなる方向に傾斜している。又、前記大径列側のリム部１６の外径は、前記外輪５の中間部の内径よりも少しだけ小さくしている。そして、本例の玉軸受１ｃを組み立てた状態で前記リム部１６の外周面を前記外輪５の中間部内周面に、全周に亙り近接対向させている。但し、これらリム部１６の外周面と外輪５の中間部内周面とは或る程度離して、これら両周面同士の間に、前記保持器１４が回転する事に対する抵抗となる油膜が形成されない様にしている。この為に本例の場合には、前記大径列側の保持器１４の径方向に関する位置決めを、前記各玉７ａと前記各ポケットの内面とを係合させる、所謂玉案内の構造により図っている。 Also, the the inner circumferential surface of the rim portion 16 of the large径列side, to form over the inclined surface 18 which is inclined in a direction in which the inner diameter increases closer to the ball 7b of the small-diameter column-side all around. In the case of this example, the inclined surface portion 18 is a combination of the steeply inclined surface portion on the inner diameter side and the gently inclined surface portion on the outer diameter side. In the illustrated example, a cylindrical surface portion is provided between the steeply inclined surface portion and the gently inclined surface portion. Of these, not only the steeply inclined surface portion but also the gently inclined surface portion is inclined in a direction in which the inner diameter increases as it approaches the ball 7b on the small diameter row side. Further, the outer diameter of the rim portion 16 on the large diameter row side is made slightly smaller than the inner diameter of the intermediate portion of the outer ring 5. In the assembled state of the ball bearing 1c of this example, the outer peripheral surface of the rim portion 16 is closely opposed to the inner peripheral surface of the intermediate portion of the outer ring 5 over the entire periphery. However, the outer peripheral surface of the rim portion 16 and the inner peripheral surface of the intermediate portion of the outer ring 5 are separated from each other to some extent, and an oil film serving as resistance against the rotation of the cage 14 is not formed between the two peripheral surfaces. Like. For this reason, in the case of this example, positioning in the radial direction of the cage 14 on the large diameter row side is achieved by a so-called ball guide structure in which the balls 7a are engaged with the inner surfaces of the pockets. Yes.

一方、前記小径列側のリム部１７の外周面に、径方向外方に突出した、フランジ状の外向鍔部１３ａを、全周に亙って形成している。そして、この外向鍔部１３ａの外周縁を、前記傾斜面部１８のうちの円筒面部乃至緩傾斜面部に対し径方向に対向させると共に、この外向鍔部１３ａの外径側端部の軸方向側面を、前記傾斜面部１８のうちの急傾斜面部に対し軸方向に対向させている。前記小径列側のリム部１７の内径は、前記内輪６の軸方向中間部でこのリム部１６の径方向内側に存在する部分の外径よりも少し大きくしている。そして、本例の玉軸受１ｃを組み立てた状態で前記リム部１７の内周面を前記内輪６の中間部外周面に、全周に亙り近接対向させている。但し、これらリム部１７の内周面と内輪６の中間部外周面とも或る程度離して、これら両周面同士の間に、前記保持器１５が回転する事に対する抵抗となる油膜が形成されない様にする。この為に、この保持器１５の径方向に関する位置決めに関しても、玉案内の構造を採用している。   On the other hand, on the outer peripheral surface of the rim portion 17 on the small diameter row side, a flange-like outward flange 13a protruding outward in the radial direction is formed over the entire circumference. Then, the outer peripheral edge of the outward flange 13a is opposed to the cylindrical surface portion or the gently inclined surface portion of the inclined surface portion 18 in the radial direction, and the axial side surface of the outer diameter side end portion of the outward flange 13a is defined. The steeply inclined surface portion of the inclined surface portion 18 is opposed in the axial direction. The inner diameter of the rim portion 17 on the small diameter row side is made slightly larger than the outer diameter of the portion existing inside the rim portion 16 in the axial direction intermediate portion of the inner ring 6. In the state where the ball bearing 1c of this example is assembled, the inner peripheral surface of the rim portion 17 is closely opposed to the outer peripheral surface of the intermediate portion of the inner ring 6 over the entire periphery. However, the inner peripheral surface of the rim portion 17 and the outer peripheral surface of the intermediate portion of the inner ring 6 are separated to a certain extent, and an oil film serving as resistance against the rotation of the cage 15 is not formed between the two peripheral surfaces. Like. For this reason, the structure of the ball guide is also adopted for the positioning of the cage 15 in the radial direction.

上述の様に構成する本例のタンデムアンギュラ型の玉軸受１ｃによれば、前記内部空間１１内に、この内部空間１１の小径側開口から入り込んだ潤滑油のうちの相当部分（前記大径列側の各玉７ａの潤滑に必要とされる量を超えた分）が、前記両リム部１６、１７の組み合わせ部分から前記小径側開口に向けて戻される。即ち、前記小径側開口から前記内部空間１１内に入り込み、この内部空間１１の軸方向中間部に達した潤滑油のうちの相当部分が、前記小径側列のリム部１７の回転に伴う遠心力により、前記外向鍔部１３ａに沿って、径方向外方に振り飛ばされる。この様にして径方向外方に振り飛ばされた潤滑油は、前記大径側列のリム部１６の内周面の前記傾斜面部１８に捕集される。更に、この傾斜面部１８に捕集された潤滑油は、前記大径側列のリム部１６の回転に伴う遠心力により、この傾斜面部１８に案内されて、前記外輪５の中間部内周面に送り出される。この際に前記潤滑油は、この傾斜面部１８に案内されつつ、前記内部空間１１の小径側開口に向かう方向の流れを惹起される。又、前記外輪５の中間部内周面には、前記リム部１６の外周面が全周に亙り近接対向して、両周面同士の間にラビリンスシールの如き構造部分を構成している。これらにより、前記傾斜面部１８から前記外輪５の中間部内周面に送り出された潤滑油のうちの多くの部分が、前記大径列側の玉７ａの設置部分に送られず、前記小径側開口から前記内部空間１１外に排出される。   According to the tandem angular ball bearing 1c of the present example configured as described above, a substantial portion of the lubricating oil that has entered the internal space 11 from the small-diameter side opening of the internal space 11 (the large diameter row). The amount exceeding the amount required for lubrication of the balls 7a on the side is returned from the combined portion of the rim portions 16 and 17 toward the small-diameter side opening. That is, a significant portion of the lubricating oil that has entered the internal space 11 through the small-diameter side opening and has reached the axially intermediate portion of the internal space 11 is subjected to centrifugal force accompanying rotation of the rim portion 17 of the small-diameter side row. Thus, it is swung away radially outward along the outward flange 13a. The lubricating oil swung away radially outward in this way is collected by the inclined surface portion 18 of the inner peripheral surface of the rim portion 16 of the large diameter side row. Further, the lubricating oil collected on the inclined surface portion 18 is guided to the inclined surface portion 18 by the centrifugal force accompanying the rotation of the rim portion 16 of the large diameter side row, and is applied to the inner peripheral surface of the intermediate portion of the outer ring 5. Sent out. At this time, the lubricating oil is induced to flow in a direction toward the small-diameter side opening of the internal space 11 while being guided by the inclined surface portion 18. Further, the outer peripheral surface of the rim portion 16 is closely opposed to the inner peripheral surface of the intermediate portion of the outer ring 5 over the entire periphery, and a structural portion such as a labyrinth seal is formed between the peripheral surfaces. As a result, many portions of the lubricating oil fed from the inclined surface portion 18 to the inner peripheral surface of the intermediate portion of the outer ring 5 are not sent to the installation portion of the balls 7a on the large diameter row side, and the small diameter side opening To the outside of the internal space 11.

上述の様に本例の構造の場合、前記小径側開口から前記内部空間１１内に入り込んだ潤滑油のうちの相当部分が、この小径側開口から排出される。前記大径列側の玉７ａの設置部分に送られる潤滑油は、前記外輪５の中間部内周面と前記リム部１６の外周面との間、並びに前記リム部１７の内周面と前記内輪６の中間部外周面との間の環状隙間を通過した必要且つ十分量のもので、過剰にはならない。この為、ピッチ円直径の大きな大径列側の玉７ａを配置した部分に過剰な潤滑油が送り込まれる事を防止して、運転時の回転抵抗（動トルク）を低く抑えられる。特に、前記大径列側の玉７ａは、前記小径列側の玉７ｂに比べて、自転速度も公転速度も速くなるが、この大径列側の玉７ａの設置部分に存在する潤滑油の量を適正にする事で、前記動トルクの低減を有効に図れる。   In the case of the structure of this example as described above, a considerable portion of the lubricating oil that has entered the internal space 11 from the small diameter side opening is discharged from the small diameter side opening. Lubricating oil sent to the installation portion of the balls 7a on the large diameter row side is between the inner peripheral surface of the intermediate portion of the outer ring 5 and the outer peripheral surface of the rim portion 16, and the inner peripheral surface of the rim portion 17 and the inner ring. It is a necessary and sufficient amount that has passed through the annular gap between the outer peripheral surface of the intermediate portion 6 and does not become excessive. For this reason, it is possible to prevent excessive lubricating oil from being fed into the portion where the balls 7a on the large diameter row side having a large pitch circle diameter are disposed, and to keep the rotational resistance (dynamic torque) during operation low. In particular, the ball 7a on the large diameter row side has a higher rotation speed and revolution speed than the ball 7b on the small diameter row side, but the lubricating oil present in the installed portion of the ball 7a on the large diameter row side is increased. By making the amount appropriate, the dynamic torque can be effectively reduced.

［実施の形態の第２例］
図２も、請求項１、２に対応する、本発明の実施の形態の第２例を示している。本例の場合には、大径列側、小径列側、両保持器１４ａ、１５ａの形状を、上述した実施の形態の第１例よりも単純化している。即ち、これら両保持器１４ａ、１５ａを、次述する傾斜面部１８ａ及び各ポケットを形成した部分を除き、単純な円筒状としている。そして、大径列側の保持器１４ａのリム部１６ａの径方向内側に、小径列側の保持器１５ａのリム部１７ａを配置している。又、このうちの大径列側の保持器１４ａのリム部１６ａの内周面に、小径列側の玉７ｂに近づくほど内径が大きくなる方向に傾斜した、傾斜面部１８ａを全周に亙り形成している。本例の場合には、この傾斜面部１８ａを、断面形状（母線）が部分円弧状の凹曲面としている。 [Second Example of Embodiment]
FIG. 2 also shows a second example of an embodiment of the present invention corresponding to claims 1 and 2. In the case of this example, the shapes of the large diameter row side, the small diameter row side, and both the retainers 14a and 15a are simplified as compared with the first example of the embodiment described above. That is, both the cages 14a and 15a are formed in a simple cylindrical shape except for the portions where the inclined surface portions 18a and the pockets described below are formed. And the rim | limb part 17a of the retainer 15a of the small diameter row | line | column side is arrange | positioned inside the rim | limb part 16a of the retainer 14a of the large diameter row | line | column side. Further, over the inner circumferential surface of the rim portion 16a of the large径列side of the cage 14a of this, inclined in the direction in which the inner diameter increases closer to the ball 7b of the small-diameter column side, the inclined surface portion 18a to the entire periphery formed doing. In the case of this example, the inclined surface portion 18a is a concave curved surface having a partial arc shape in cross section (bus line).

本例の場合も、前記両保持器１４ａ、１５ａの径方向に関する位置決めを、玉７ａ、７ｂの転動面と前記各ポケットの内面との係合により図る、玉案内の構造を採用している。この様な玉案内の構造を採用し、且つ、前記両保持器１４ａ、１５ａとして単純な形状を採用した場合でも、前記大径列側の保持器１４ａのリム部１６ａの径方向内側に、前記小径列側の保持器１５ａのリム部１７ａを配置できる様にする為、これら両リム部１６ａ、１７ａの設置位置を、前記両列の玉７ａ、７ｂのピッチ円に対し、径方向にオフセットさせている。即ち、前記大径列側の保持器１４ａのリム部１６ａに関しては、図２に多少誇張して示す様に、ピッチ円よりも径方向外寄り部分の厚さＴ１を、同じく径方向内寄り部分の厚さｔ１よりも大きく（Ｔ１＞ｔ１）している。これに対して、前記小径列側の保持器１５ａのリム部１７ａに関しては、やはり図２に多少誇張して示す様に、ピッチ円よりも径方向内寄り部分の厚さＴ２を、同じく径方向外寄り部分の厚さｔ２よりも大きく（Ｔ２＞ｔ２）している。 Also in the case of this example, a ball guide structure is adopted in which positioning in the radial direction of both the retainers 14a and 15a is achieved by engagement between the rolling surfaces of the balls 7a and 7b and the inner surfaces of the pockets. . Even when such a ball guide structure is adopted and a simple shape is adopted as both the retainers 14a and 15a, the rim portion 16a of the retainer 14a on the large diameter row side is radially inward. In order to be able to arrange the rim portion 17a of the cage 15a on the small diameter row side, the installation positions of both the rim portions 16a, 17a are offset in the radial direction with respect to the pitch circles of the balls 7a, 7b in both rows. ing. That is, the terms are rim portion 16a of the large径列side of the cage 14a, as shown somewhat exaggerated in FIG. 2, the thickness T 1 of the radially outer portion closer the pitch circle, likewise radially inboard It is larger than the thickness t 1 of the portion (T 1 > t 1 ). In contrast, with respect to the rim portion 17a of the small diameter column-side of the cage 15a, also as shown somewhat exaggerated in Figure 2, the radially inner portion closer the pitch circle of the thickness T 2, likewise diameter It is larger than the thickness t 2 of the portion outside the direction (T 2 > t 2 ).

本例の場合には、前記小径列側の保持器１５ａの回転に伴って、この保持器１５ａのリム部１７ａから径方向外方に振り飛ばされた潤滑油が、前記傾斜面部１８ａに捕集されて、内部空間１１の小径側開口部に戻される。
その他の部分の構成及び作用は、前述した実施の形態の第１例と同様であるから、重複する説明は省略する。 In the case of this example, as the retainer 15a on the small-diameter row side rotates, the lubricating oil sprinkled radially outward from the rim portion 17a of the retainer 15a is collected on the inclined surface portion 18a. Then, the inner space 11 is returned to the small diameter side opening.
Since the configuration and operation of the other parts are the same as those in the first example of the above-described embodiment, redundant description is omitted.

［実施の形態の第３例］
図３も、請求項１、２に対応する、本発明の実施の形態の第３例を示している。本例の場合には、大径列側の保持器１４ｂのリム部１６ｂの内周面に、断面形状（母線）が直線状である、傾斜面１８ｂを全周に亙り形成している。又、本例の場合には、前記保持器１４ｂの形状を、軸方向に関し対称にして、この保持器１４ｂの組み付け方向が限定されない様にしている。
その他の部分の構成及び作用は、上述した実施の形態の第２例と同様であるから、重複する説明は省略する。 [Third example of embodiment]
FIG. 3 also shows a third example of an embodiment of the present invention corresponding to claims 1 and 2. In the case of this example, an inclined surface 18b having a linear cross-sectional shape (bus line) is formed over the entire circumference on the inner peripheral surface of the rim portion 16b of the cage 14b on the large diameter row side. In the case of this example, the shape of the cage 14b is symmetric with respect to the axial direction so that the assembling direction of the cage 14b is not limited.
Since the configuration and operation of the other parts are the same as in the second example of the above-described embodiment, a duplicate description is omitted.

［実施の形態の第４例］
図４は、請求項１、３に対応する、本発明の実施の形態の第４例を示している。本例の場合には、１対の保持器１４ｃ、１５ｂの断面形状を楔状としている。言い換えれば、これら両保持器１４ｃ、１５ｂの径方向に関する厚さを、軸方向に関して漸次変化させている。そして、それぞれの径方向に関する厚さが大きくなった部分を、両列の玉７ａ、７ｂの間部分に配置している。又、本例の場合には、大径列側の保持器１４ｃのリム部１６ｃの内周面に傾斜面部１８ｃを全周に亙り形成するだけでなく、小径列側の保持器１５ｂのリム部１７ｂの外周面にも傾斜面部１９を全周に亙り形成している。この傾斜面部１９は、径方向外方に向かうほど、前記保持器１５ｂの軸方向中央部に向かう方向に傾斜している。そして、前記両傾斜面部１８ｃ、１９を、径方向及び軸方向に重畳する状態で、互いに対向させている。 [Fourth Example of Embodiment]
FIG. 4 shows a fourth example of an embodiment of the present invention corresponding to claims 1 and 3 . In the case of this example, the cross-sectional shape of the pair of cages 14c and 15b is a wedge shape. In other words, the thickness in the radial direction of both the cages 14c and 15b is gradually changed in the axial direction. And the part where the thickness regarding each radial direction became large is arrange | positioned in the part between the balls 7a and 7b of both rows. In the case of this example, not only the inclined surface portion 18c is formed over the entire circumference of the rim portion 16c of the retainer 14c on the large diameter row side, but also the rim portion of the retainer 15b on the small diameter row side. An inclined surface portion 19 is formed over the entire circumference on the outer peripheral surface of 17b. The inclined surface portion 19 is inclined in the direction toward the axial central portion of the cage 15b as it goes outward in the radial direction. And both the said inclined surface parts 18c and 19 are made to oppose each other in the state which overlaps with radial direction and an axial direction.

上述の様に構成する本例の場合には、内部空間１１の小径側開口からこの内部空間１１内に送り込まれた潤滑油のうち、前記小径列側の保持器１５ｂのリム部１７ｂに達した潤滑油が、この保持器１５ｂの回転に伴う遠心力により、前記両傾斜面部１８ｃ、１９同士の間部分に存在する、傾斜空間２０内に、この傾斜空間２０の内径側開口から入り込む。この傾斜空間２０内に入り込んだ潤滑油は、前記両保持器１４ｃ、１５ｂの回転に伴う遠心力によりこの傾斜空間２０内を径方向外方に流れ、この傾斜空間２０の外径側開口から外輪５の内周面に向け噴き出す。この様にして、この外輪５の内周面に噴き出す潤滑油の流れには、前記内部空間１１の小径側開口に向かう方向の分力が存在する。この為、前記大径側のリム部１６ｃの外周面を外輪５の中間部内周面に近接させたり、前記小径側のリム部１７ｂの内周面を前記内輪６の中間部外周面に近接させたりしなくても、潤滑油の余剰分が大径列側の玉７ａ部分に送られる事を防止できる。
その他の部分の構成及び作用は、前述した実施の形態の第３例と同様であるから、重複する説明は省略する。 In the case of this example configured as described above, the lubricating oil fed into the internal space 11 from the small-diameter side opening of the internal space 11 has reached the rim portion 17b of the cage 15b on the small-diameter row side. Lubricating oil enters into the inclined space 20 existing between the two inclined surface portions 18c and 19 from the inner diameter side opening of the inclined space 20 by the centrifugal force accompanying the rotation of the cage 15b. The lubricating oil that has entered the inclined space 20 flows radially outward in the inclined space 20 due to the centrifugal force associated with the rotation of the cages 14c and 15b, and the outer ring is opened from the outer diameter side opening of the inclined space 20. It spouts toward the inner peripheral surface of 5. In this way, there is a component force in the direction toward the small-diameter side opening of the internal space 11 in the flow of the lubricating oil sprayed to the inner peripheral surface of the outer ring 5. For this reason, the outer peripheral surface of the rim portion 16c on the large diameter side is brought close to the inner peripheral surface of the intermediate portion of the outer ring 5, or the inner peripheral surface of the rim portion 17b on the smaller diameter side is brought close to the outer peripheral surface of the intermediate portion of the inner ring 6. Even if it does not, it can prevent that the excess part of lubricating oil is sent to the ball 7a part by the side of a large diameter row.
Since the configuration and operation of the other parts are the same as in the third example of the above-described embodiment, a duplicate description is omitted.

［本発明に関する参考例］
図５は、本発明に関する参考例を示している。本参考例の場合には、両列の玉７ａ、７ｂを保持した１対の保持器１４ｄ、１５ｃを構成し、これら両列の玉７ａ、７ｂ同士の間に存在するリム１６ｄ、１７ｃを、それぞれこれら各玉７ａ、７ｂを転動自在に保持する為のポケットを設けた本体部分２１ａ、２１ｂよりも径方向に関する幅寸法が大きくなったフランジ状としている。そして、それぞれがフランジ状である前記両リム部１６ｄ、１７ｃのうち、大径列側のリム部１６ｄの外周縁と、外輪５の中間部の内周面とを近接させている。又、小径列側のリム部１７ｃの内周縁と、内輪６の中間部外周面とを近接させている。 [ Reference Example for the Present Invention ]
FIG. 5 shows a reference example related to the present invention . In the case of this reference example , a pair of retainers 14d and 15c holding both rows of balls 7a and 7b are configured, and the rims 16d and 17c existing between these rows of balls 7a and 7b are Each of the balls 7a and 7b has a flange shape having a larger width dimension in the radial direction than the main body portions 21a and 21b provided with pockets for holding the balls 7a and 7b in a freely rollable manner. Of the two rim portions 16 d and 17 c each having a flange shape, the outer peripheral edge of the rim portion 16 d on the large diameter row side and the inner peripheral surface of the intermediate portion of the outer ring 5 are brought close to each other. Further, the inner peripheral edge of the rim portion 17c on the small diameter row side and the intermediate outer peripheral surface of the inner ring 6 are brought close to each other.

この様な構成を有する本参考例の構造の場合には、前記両リム部１６ｄ、１７ｃが、内部空間１１内に入り込んだ潤滑油が、この内部空間１１を貫流しつつ流れる事を防止する。この為、前記各玉７ａ、７ｂの転動面と、両外輪軌道９ａ、９ｂ及び両内輪軌道１０ａ、１０ｂとの転がり接触部に過剰な潤滑油が存在する事を防止して、運転時の回転抵抗（動トルク）を低く抑えられる。特に、小径列側の前記各玉７ｂに比べて、自転速度も公転速度も速くなる、大径列側の前記各玉７ａの設置部分に存在する潤滑油の量を適正にする事で、前記動トルクの低減を有効に図れる。 In the case of the structure of this reference example having such a configuration, the rim portions 16d and 17c prevent the lubricating oil that has entered the internal space 11 from flowing through the internal space 11. For this reason, it is possible to prevent excessive lubricating oil from being present at the rolling contact portions between the rolling surfaces of the balls 7a and 7b and the outer raceways 9a and 9b and the inner raceways 10a and 10b. The rotational resistance (dynamic torque) can be kept low. In particular, compared to the balls 7b on the small diameter row side, both the rotation speed and the revolution speed are increased, and by making the amount of lubricating oil present in the installed portion of the balls 7a on the large diameter row side appropriate, It is possible to effectively reduce the dynamic torque.

［実施の形態の第５例］
図６は、請求項１、３に対応する、本発明の実施の形態の第５例を示している。本例の場合には、外輪５の内周面のうち、１対の外輪軌道９ａ、９ｂに隣接するカウンターボア部２２ａ、２２ｂの一部（小径側端部）で、これら両外輪軌道９ａ、９ｂに隣接する部分の内径を、各玉７ａ、７ｂの外接円の直径よりも少しだけ小さくしている。そして、これら両隣接する部分を、それぞれ係り代部２３ａ、２３ｂとしている。それぞれ保持器１４ｃ、１５ｂにより保持された前記各玉７ａ、７ｂを、前記両外輪軌道９ａ、９ｂの内径側に配置した状態では、これら各玉７ａ、７ｂと前記両係り代部２３ａ、２３ｂとの（前記両保持器１４ｃ、１５ｂの弾性に基づく）係合により、前記各玉７ａ、７ｂが前記外輪５の内径側から不用意に抜け出る事が防止される。前記両係り代部２３ａ、２３ｂの内径を、前記両保持器１４ｃ、１５ｂと干渉しない範囲に規制する事は勿論である。 [ Fifth Example of Embodiment]
FIG. 6 shows a fifth example of an embodiment of the present invention corresponding to claims 1 and 3 . In the case of this example, a part of the counter bore portions 22a, 22b (small-diameter side end portions) adjacent to the pair of outer ring raceways 9a, 9b on the inner peripheral surface of the outer ring 5, these outer ring raceways 9a, The inner diameter of the portion adjacent to 9b is slightly smaller than the diameter of the circumscribed circle of each ball 7a, 7b. These two adjacent portions are used as dependency margin portions 23a and 23b, respectively. In a state where the balls 7a and 7b held by the cages 14c and 15b are arranged on the inner diameter side of the outer ring raceways 9a and 9b, the balls 7a and 7b and the engagement margins 23a and 23b, The engagement (based on the elasticity of the two cages 14c and 15b) prevents the balls 7a and 7b from being inadvertently pulled out from the inner diameter side of the outer ring 5. It goes without saying that the inner diameters of both the engagement margins 23a and 23b are restricted to a range that does not interfere with both the retainers 14c and 15b.

本例の場合には、前記両係り代部２３ａ、２３ｂの存在により、前記各玉７ａ、７ｂと前記外輪５とを一体的に（非分離状態で）取り扱う事ができて、タンデムアンギュラ型玉軸受の組み付け作業の容易化を図れる。尚、内輪６に関しては、前記外輪５及び前記各玉７ａ、７ｂを外径側部材（例えばハウジング）の内径側に組み付けてから、これら各玉７ａ、７ｂの内径側に、軸方向変位に基づいて組み付ける。この際、これら各玉７ａ、７ｂは、殆ど径方向外側に変位する事はない。従って、前記内輪６の外周面には、前記係り代部１９ａ、１９ｂに対応する構造は設けていない。
その他の部分の構成及び作用は、前述した実施の形態の第４例と同様であるから、同等部分には同一符号を付して、重複する説明を省略する。
尚、本例の様に、外輪５の内周面に係り代部を設ける構造は、図４に示した実施の形態の第４例の構造に限らず、前述の図１〜３、５に示した実施の形態の第１〜３例及び参考例の構造と組み合わせて実施する事もできる。 In the case of this example, the balls 7a, 7b and the outer ring 5 can be handled integrally (in a non-separated state) due to the presence of both the interlocking margins 23a, 23b, and a tandem angular ball The assembly work of the bearing can be facilitated. Regarding the inner ring 6, the outer ring 5 and the balls 7a and 7b are assembled on the inner diameter side of an outer diameter side member (for example, a housing), and then the inner diameter side of each of the balls 7a and 7b is based on the axial displacement. Assemble. At this time, these balls 7a and 7b are hardly displaced outward in the radial direction. Therefore, the outer ring surface of the inner ring 6 is not provided with a structure corresponding to the engagement margins 19a and 19b.
Since the configuration and operation of the other parts are the same as those in the fourth example of the embodiment described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.
As in this example, the structure in which the engagement margin is provided on the inner peripheral surface of the outer ring 5 is not limited to the structure of the fourth example of the embodiment shown in FIG. It can also be implemented in combination with the structures of the first to third examples and the reference example of the illustrated embodiment.

本発明のタンデムアンギュラ型玉軸受は、大きなラジアル荷重及びスラスト荷重が加わった状態で回転する回転軸を支承する部分であれば、図７に示した自動車用のデファレンシャルギヤや、トランスファ等の自動車用の動力伝達装置に限らず、一般機械を含めて、各種回転機械装置の回転支持部分に組み込んだ状態で使用できる。   The tandem angular contact ball bearing of the present invention is a part for supporting a rotating shaft that rotates in a state where a large radial load and a thrust load are applied. It can be used in the state incorporated in the rotation support part of various rotary machine devices including not only the power transmission device but also general machines.

例えば、自動変速機（ＡＴ）、手動変速機（ＭＴ）、ダブルクラッチトランスミッション（ＤＣＴ）等の自動車用変速機を構成する、インプットシャフト、カウンターシャフト、アウトプットシャフト等の回転軸の回転支持部に使用する事もできる。エンジンの出力を駆動輪に伝達する為の自動車用変速機は、エンジンルーム内、フロアトンネル内等の限られた空間内に設置される。又、近年に於ける、変速機の高効率化（例えば変速段の多段化）に伴って、低トルク化の要求に関しても、より厳しくなっている。この為、自動車用変速機の回転支持部に使用する転がり軸受に関しても、小型且つ高負荷容量で、しかも動トルクが低いものが要求される。この様な要求に対して、本発明のタンデムアンギュラ型玉軸受は、極めて有効である。   For example, used for rotation support parts of rotating shafts such as input shafts, counter shafts, output shafts, etc. constituting automobile transmissions such as automatic transmission (AT), manual transmission (MT), double clutch transmission (DCT) You can also do it. An automobile transmission for transmitting engine output to drive wheels is installed in a limited space such as an engine room or a floor tunnel. In recent years, with the increase in efficiency of transmissions (for example, the increase in the number of shift stages), the demand for lower torque has become more severe. For this reason, a rolling bearing used for a rotation support portion of an automobile transmission is also required to have a small size, a high load capacity, and a low dynamic torque. The tandem angular ball bearing of the present invention is extremely effective for such a demand.

１、１ａ、１ｂ、１ｃ 玉軸受
２ 玉軸受
３ ピニオン軸
４ ピニオンギヤ
５ 外輪
６ 内輪
７ａ、７ｂ 玉
８ａ、８ｂ、８ｂ´ 保持器
９ａ、９ｂ 外輪軌道
１０ａ、１０ｂ 内輪軌道
１１ 内部空間
１２ａ、１２ｂ シールリング
１３、１３ａ 外向鍔部
１４、１４ａ、１４ｂ、１４ｃ、１４ｄ 保持器
１５、１５ａ、１５ｂ、１５ｃ 保持器
１６、１６ａ、１６ｂ、１６ｃ、１６ｄ リム部
１７、１７ａ、１７ｂ、１７ｃ リム部
１８、１８ａ、１８ｂ、１８ｃ 傾斜面部
１９ 傾斜面部
２０ 傾斜空間
２１ａ、２１ｂ 本体部分
２２ａ、２２ｂ カウンターボア部
２３ａ、２３ｂ 係り代部 1, 1a, 1b, 1c Ball bearing 2 Ball bearing 3 Pinion shaft 4 Pinion gear 5 Outer ring 6 Inner ring 7a, 7b Ball 8a, 8b, 8b 'Cage 9a, 9b Outer ring raceway 10a, 10b Inner ring raceway 11 Internal space 12a, 12b Seal Ring 13, 13a Outward flange 14, 14a, 14b, 14c, 14d Cage 15, 15a, 15b, 15c Cage 16, 16a, 16b, 16c, 16d Rim part 17, 17a, 17b, 17c Rim part 18, 18a , 18b, 18c Inclined surface portion 19 Inclined surface portion 20 Inclined space 21a, 21b Main body portion 22a, 22b Counter bore portion 23a, 23b

Claims (3)

それぞれがアンギュラ型であって内径が互いに異なる２列の外輪軌道を内周面に、互いに同じ向きに設けた外輪と、それぞれがアンギュラ型であって外径が互いに異なる２列の内輪軌道を外周面に、互いに同じ向きに設け、前記外輪の内径側にこの外輪と同心に配置された内輪と、前記両外輪軌道と前記両内輪軌道との間に、それぞれの列毎に複数個ずつ、両列同士の間で同じ方向の接触角を付与され、且つ、ピッチ円直径を互いに異ならせた状態で転動自在に設けられた玉と、これら各玉を転動自在に保持した、両列毎に互いに独立して直径が互いに異なる１対の保持器とを備えたタンデムアンギュラ型玉軸受に於いて、前記ピッチ円直径が大きい大径列側の玉を転動自在に保持する為の大径側保持器を構成する円環状の大径側リム部が、前記ピッチ円直径が小さい小径列側の玉に対向する部分に設けられており、この小径列側の玉を転動自在に保持する為の小径側保持器を構成する円環状の小径側リム部が、前記大径側リム部の径方向内側に配置されており、この大径側リム部の内周面が全周に亙り、前記小径列側の玉に近づくほど内径が大きくなる方向に傾斜している事で、この小径列側の玉を配置した部分から前記大径列側の玉を配置した部分に向かう潤滑油の一部を、この小径列側に戻す事を特徴とするタンデムアンギュラ型玉軸受。 Two outer ring raceways each having an angular shape and different inner diameters on the inner peripheral surface, outer rings provided in the same direction, and two rows of inner ring raceways each having an angular shape and different outer diameters on the outer periphery A plurality of inner rings arranged in the same direction on the inner surface of the outer ring and arranged concentrically with the outer ring on the inner diameter side of the outer ring, and the outer ring raceway and the inner ring raceways in a plurality of rows. Balls provided with a contact angle in the same direction between the rows and having a pitch circle diameter different from each other and capable of rolling, and each row holding these balls so as to roll In a tandem angular contact ball bearing having a pair of cages having different diameters independently from each other, a large diameter for holding the balls on the large diameter row side having a large pitch circle diameter in a freely rolling manner An annular large-diameter side rim constituting the side cage is Serial provided a ball facing portion of the pitch circle diameter is smaller diameter column-side, small-diameter side rim portion of the annular constituting the small diameter side cage for holding the balls of the small diameter column side rollably However, the inner peripheral surface of the large-diameter rim portion extends over the entire circumference, and the inner diameter increases toward the balls on the small-diameter row side. by you are, tandem angular contact, characterized in that a portion from the portion of arranging the balls of the small diameter column-side of the lubricating oil toward the ball was placed part of the large径列side, back to the small diameter column-side Type ball bearing. 前記大径側リム部の外周面が、前記外輪の内周面に全周に亙り近接対向している、請求項１に記載したタンデムアンギュラ型玉軸受。 2. The tandem angular ball bearing according to claim 1 , wherein an outer peripheral surface of the large-diameter side rim portion is closely opposed to an inner peripheral surface of the outer ring over the entire circumference . 前記小径側リム部の外周面が、径方向外方に向かうほど、前記小径側保持器の軸方向中央部に向かう方向に傾斜しており、前記小径側リム部の外周面と前記大径側リム部の内周面とを、径方向及び軸方向に重畳する状態で互いに対向させている、請求項１に記載したタンデムアンギュラ型玉軸受。 The outer peripheral surface of the small-diameter side rim portion is inclined in a direction toward the axial central portion of the small-diameter side retainer as it goes radially outward, and the outer peripheral surface of the small-diameter side rim portion and the large-diameter side The tandem angular ball bearing according to claim 1, wherein the inner peripheral surface of the rim portion is opposed to each other in a state of overlapping in the radial direction and the axial direction .
JP2011092584A 2010-04-19 2011-04-19 Tandem angular contact ball bearings Active JP5803234B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2011092584A JP5803234B2 (en) 2010-04-19 2011-04-19 Tandem angular contact ball bearings

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2010096293 2010-04-19
JP2010096293 2010-04-19
JP2011092584A JP5803234B2 (en) 2010-04-19 2011-04-19 Tandem angular contact ball bearings

Publications (2)

Publication Number Publication Date
JP2011241978A JP2011241978A (en) 2011-12-01
JP5803234B2 true JP5803234B2 (en) 2015-11-04

Family

ID=45408835

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2011092584A Active JP5803234B2 (en) 2010-04-19 2011-04-19 Tandem angular contact ball bearings

Country Status (1)

Country Link
JP (1) JP5803234B2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014215739B4 (en) 2014-08-08 2020-06-04 Aktiebolaget Skf Double row gear bearing comprising a bearing cage assembly and gear

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10239742B4 (en) * 2002-05-10 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Single-sided double angular contact ball bearings
JP4285017B2 (en) * 2002-12-19 2009-06-24 株式会社ジェイテクト Differential equipment
JP4862458B2 (en) * 2006-04-03 2012-01-25 株式会社ジェイテクト Double-row rolling bearing for pinion shaft support and rolling bearing device provided with the same
JP2009287626A (en) * 2008-05-28 2009-12-10 Jtekt Corp Rolling bearing device
JP2010007788A (en) * 2008-06-27 2010-01-14 Jtekt Corp Double row ball bearing and pinion shaft support device for vehicle
JP5126678B2 (en) * 2008-07-25 2013-01-23 株式会社ジェイテクト Rolling bearing

Also Published As

Publication number Publication date
JP2011241978A (en) 2011-12-01

Similar Documents

Publication Publication Date Title
JP4285017B2 (en) Differential equipment
JP5375969B2 (en) Rotation support device for pinion shaft
JP2016109253A (en) Rolling bearing
JP2006266277A (en) Self-aligning roller bearing with cage
JP5636887B2 (en) Tandem angular contact ball bearings
JP6171444B2 (en) Rolling bearing device and pinion shaft support device for vehicle
JP2010255778A (en) Radial needle bearing
JP5927773B2 (en) Tandem angular contact ball bearings
JP5803234B2 (en) Tandem angular contact ball bearings
JP2011094716A (en) Thrust roller bearing
CN107269689A (en) A kind of combination bearing suitable for the dish-shaped traction machine of elevator
US9897195B2 (en) Planetary gear drive
JP4003247B2 (en) Rolling bearing device with oil supply means
JP6064783B2 (en) Rolling bearing
JP5600926B2 (en) Tandem type double row angular contact ball bearing
JP2008045597A (en) Tapered roller bearing and pilot portion shaft supporting structure
JP2005188679A (en) Ball bearing
JP2011196393A (en) Thrust roller bearing
JP6759544B2 (en) Thrust roller bearing
JP2008111505A (en) Thrust needle roller bearing
JP2011163387A (en) Tapered roller bearing
JP2009210078A (en) Self-aligning roller bearing
JP2015068354A (en) Rolling bearing
JP2016011667A (en) Spacer for radial needle bearing
JP5991114B2 (en) Tapered roller bearing and assembly method thereof

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20140411

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20141212

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20150120

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20150318

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20150804

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20150817

R150 Certificate of patent (=grant) or registration of utility model

Ref document number: 5803234

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150