JP4321092B2 - Double row tapered roller bearing - Google Patents

Double row tapered roller bearing Download PDF

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Publication number
JP4321092B2
JP4321092B2 JP2003101606A JP2003101606A JP4321092B2 JP 4321092 B2 JP4321092 B2 JP 4321092B2 JP 2003101606 A JP2003101606 A JP 2003101606A JP 2003101606 A JP2003101606 A JP 2003101606A JP 4321092 B2 JP4321092 B2 JP 4321092B2
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Japan
Prior art keywords
row
outer ring
lubricating oil
roller bearing
tapered roller
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Expired - Fee Related
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JP2003101606A
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Japanese (ja)
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JP2004308738A (en
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雄太 濱口
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
    • 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

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double row conical roller bearing having superior lubricating performance suitable for the application environment by positively supplying lubricant to either of rows. <P>SOLUTION: This double row conical roller bearing comprises a pair of inner rings 11, 12 having inner raceway surfaces 13, 14, an outer ring 15 having outer ring raceway surfaces 16, 17, a plurality of rolling elements 18 relatively rotatably mounted among the inner and outer ring raceway surfaces 13, 14, 16, 17, and a pair of retainers 19, 20 rotatably retaining the rolling elements 18, and has an oil groove 23 for supplying the lubricant on a butting face 22 of the pair of inner rings 11, 12. The butting face 22 of the inner rings 11, 12 is shifted to a bearing end face 11a side with respect to an intermediate position of both retainers 19, 20. <P>COPYRIGHT: (C)2005,JPO&amp;NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、例えば自動車用自動変速機のリング歯車を回転軸に対して回転自在に支持するのに用いられる複列円すいころ軸受に関し、詳しくは潤滑油供給用の油溝を有する複列円すいころ軸受に関する。
【０００２】
【従来の技術】
上記の複列円すいころ軸受として、図３に示す複列円すいころ軸受５０は、複列の外輪軌道５２，５２を有する外輪５１、内輪軌道５４，５４を有する内輪５３，５３、転動体５５、保持器５６，５６を有し、遊星歯車式自動変速機の遊星歯車機構において、回転軸５７と、回転軸５７の中間部外周面に配されたハウジング５８との間に配されている。複列円すいころ軸受５０は、また、外輪５１の軸方向中間部内周面で外輪軌道５２，５２の間に凹溝５９が円周方向に亙って設けられている。凹溝５９は、内輪５３，５３の突き合わせ端面部に形成された切り欠き６０，６０から吐出された潤滑油を一時的に貯留する。
【０００３】
このような複列円すいころ軸受５０は、切り欠き６０，６０を通じて内輪５３，５３の軸方向中間部で内輪軌道５４，５４の間部分から吐出した潤滑油を、円周方向に亙って広く分配することによって、切り欠き６０，６０を直径方向内側から外側に流れ、回転軸５７の外周面から吐出した潤滑油が、回転に伴う遠心力の影響で周囲に飛散し、そのうちの一部が凹溝５９に捕集される（例えば、特許文献１参照）。
【０００４】
【特許文献１】
特開平１０−２７４２４３号公報（第４−５頁、第１図）
【０００５】
【発明が解決しようとする課題】
ところが、上記特許文献１に記載された複列円すいころ軸受５０では、内輪５３，５３の突き合わせ端面部が両保持器５６，５６の中間に配置されており、そして内輪５３，５３の突き合わせ端面部に形成された切り欠き６０，６０から吐出された潤滑油は、円周方向に亙って広く分配される。しかし、実際に複列円すいころ軸受が用いられる環境において、各列における潤滑油の必要量は異なっているが、上記の複列円すいころ軸受５０では、必要量に応じて潤滑油をいずれか一方の列に振り分けることは困難である。
【０００６】
本発明は、上記問題に鑑みてなされたものであり、潤滑油をいずれか一方の列に積極的に供給すことによって、組み付けられる環境に応じた優れた潤滑性能を備えた複列円すいころ軸受を提供することを目的とする。
【０００７】
【課題を解決するための手段】
本発明の請求項１記載の複列円すいころ軸受は、それぞれ内輪軌道面を有する一対の内輪と、外輪軌道面を有する外輪と、前記内輪軌道面及び前記外輪軌道面間に相対回転自在に配された複数の転動体と、前記転動体を転動自在に保持する一対の保持器と、を有し、前記一対の内輪の突き合わせ面に潤滑油供給用の油溝を有する複列円すいころ軸受であって、前記潤滑油供給用の油溝が、前記両保持器の中間位置より軸受端面側にオフセットして、軸方向において前記一対の保持器の一方の小径リング部よりポケット側に配され、これにより、複列のうちの一方の列における潤滑油の必要量を、他方の列における潤滑油の必要量よりも多く設定することを特徴とする。
【０００８】
前記構成の複列円すいころ軸受によれば、両保持器の中間位置より軸受端面側にオフセットした位置に一対の内輪の突き合わせ面が配される。
したがって、複列のうちの一方の列における潤滑油の必要量を、他方の列における潤滑油の必要量よりも多く設定する組付環境に対しては、内輪の突き合わせ面を、一方の列に配される一方の保持器と他方の列に配される他方の保持器との中間位置より一方の列の内輪における軸受端面側に配置することにより、油溝を通じて供給される潤滑油が一方の保持器で受け取られ、一方の列の軸受空間にのみ集中して供給されることになり、一方の列を積極的に潤滑する。また、他方の列に対しては、一方の列に供給されなかった潤滑油が供給される。これにより、潤滑油をいずれか一方の列に積極的に供給することができ、組み付けられる環境に応じた優れた潤滑性能を有する複列円すいころ軸受を提供することができる。
【０００９】
【発明の実施の形態】
以下、本発明の複列円すいころ軸受の実施の形態例を図１及び図２に基づいて詳細に説明する。
【００１０】
図１は本発明に係る複列円すいころ軸受の第１実施形態を示す半断面図、図２は本発明に係る複列円すいころ軸受の第２実施形態を示す半断面図である。なお、第２実施形態において、既に説明した部材等と同様な構成・作用を有する部材等については、図中に同一符号または相当符号を付することにより、説明を簡略化或いは省略する。
【００１１】
図１に示すように、第１実施形態の複列円すいころ軸受１０は、内輪軌道面１３，１４を有する内輪１１，１２と、外輪軌道面１６，１７を有する外輪１５と、内輪軌道面１３と外輪軌道面１６および内輪軌道面１４と外輪軌道面１７との間にそれぞれ相対回転自在に配された複数の円すいころ１８と、円すいころ１８を転動自在に保持する一対の保持器１９，２０と、から構成されている。この複列円すいころ軸受１０は、内輪１１，１２が背面合わせである。
【００１２】
内輪１１，１２のうち、図１中の左方側に配された内輪１２は、内輪軌道面１４が形成された外周面に、図１中の右方側に配された内輪１１に向けて延出した延長部２１が形成されている。そのため、内輪１２は、軸方向長さＬ１が、内輪１１の軸方向長さＬ２よりも長くなっている。すなわち、内輪１１と内輪１２との突き合わせ面２２が、内輪軌道面１３，１４（または外輪軌道面１６，１７）の中間位置より軸受端面側にオフセットして配置されている。
【００１３】
内輪１１及び内輪１２の突き合わせ面２２側の端部には、油溝２３が形成されている。油溝２３は、突き合わせ面２２に対応して円周方向に配されている。油溝２３は、軸方向長さＬ２の内輪１１と軸方向長さＬ１の内輪１２との突き合わせ面２２に形成されており、軸受中心線ａ１に対して一方の内輪１１の端面１１ａ側に寄って配置されている。これらの内輪１１，１２には、遊星歯車式自動変速機の遊星歯車機構における回転軸が内嵌される。ここで、油溝２３は、突き合わせ面２２においてＶ字状の溝形状にされている。
【００１４】
外輪１５は、一方の外輪軌道面１６が一方の列に配され、他方の外輪軌道面１７が他方の列に配されている。外輪１５は、遊星歯車式自動変速機の遊星歯車機構におけるハウジングに内嵌される。
【００１５】
内輪１１，１２の内輪軌道面１３，１４と、外輪１５の外輪軌道面１６，１７と、円すいころ１８とは、それぞれの円錐面の延長上の頂点が軸線上の１点に集まるように設定されている。内輪１１，１２の内輪軌道面１３，１４は、円すいころ１８のアキシアル方向の移動を規制する。
【００１６】
保持器１９，２０は、鋼板製のかご形プレス保持器であり、大径リング部１９ａ，２０ａと、小径リング部１９ｂ，２０ｂとの間において、円すいころ１８の形状に対応して打ち抜かれた等脚台形のポケット１９ｃ，２０ｃが円周方向に複数配されている。保持器１９，２０は、中間位置に一致する軸受中心線ａ１を挟んで対向して配されているため、外輪１５の一方の外輪軌道面１６に対応して一方の保持器１９が配され、他方の外輪軌道面１７に対応して他方の保持器２０が配されている。保持器１９，２０は、それらの内周部が他方の内輪１２の外周面に加締めにより固定されている。
【００１７】
一方の保持器１９が、外輪１５の一方の外輪軌道面１６に対応して配され、他方の保持器２０が、他方の外輪軌道面１７に対応して配されているため、一方の保持器１９が、軸受中心線ａ１に対して一方の内輪１１の端面１１ａ側に寄って配置された油溝２３から供給される潤滑油を積極的に受け止めるように機能する。
【００１８】
上述した複列円すいころ軸受１０は、内輪１１，１２に主軸が内嵌され、外輪１５がハウジングに内嵌されることによって、遊星歯車式自動変速機の遊星歯車機構に組み付けられる。遊星歯車式自動変速機が作動されることにより主軸が回転されると、外部の潤滑油供給手段から油溝２３に潤滑油が送給され、油溝２３から軸受空間内に潤滑油が流れ出す。そのとき、潤滑油は、内輪１１，１２が回転することによる遠心力や送給圧力によって油溝２３から軸受外周方向に流れ、流れた潤滑油が一方の保持器１９に衝突する。そして、一方の保持器１９に衝突した潤滑油が、外輪１５の一方の外輪軌道面１６，一方の内輪１１の内輪軌道面１３，外輪軌道面１６と内輪軌道面１３とにより支持されている円すいころ１８とからなる一方の列に多く供給される。
【００１９】
同時に、一方の保持器１９に衝突しなかった残りの潤滑油が、外輪１５の他方の外輪軌道面１７，他方の内輪１２の内輪軌道面１４，外輪軌道面１７と内輪軌道面１４とにより支持されている円すいころ１８とからなる他方の列に供給される。つまり、複列のうちの一方の列における潤滑油の必要量を、他方の列における潤滑油の必要量よりも多く設定される組付環境に対応して潤滑油が振り分けられる。
【００２０】
以上、第１実施形態の複列円すいころ軸受１０によれば、両保持器１９，２０の中間位置に一致する軸受中心線ａ１より軸受端面１１ａ側にオフセットした位置に一対の内輪１１，１２の突き合わせ面２２が配される。
したがって、複列のうちの一方の列における潤滑油の必要量を、他方の列における潤滑油の必要量よりも多く設定する組付環境に対しては、内輪１１，１２の突き合わせ面２２を、一方の列に配される一方の保持器１９と他方の列に配される他方の保持器２０との中間位置より一方の列の内輪１１における軸受端面１１ａ側に配置することにより、油溝２３を通じて供給される潤滑油が一方の保持器１９で受け取られ、一方の列の軸受空間にのみ集中して供給されて一方の列を積極的に潤滑する。また、他方の列に対しては、一方の列に供給されない潤滑油が供給される。これにより、潤滑油をいずれか一方の列に積極的に供給することにより組み付けられる環境に対応して優れた潤滑性能を有する複列円すいころ軸受１０を提供することができる。
【００２１】
次に、図２を用いて本発明に係る第２実施形態を説明する。
図２に示すように、第２実施形態に係る複列円すいころ軸受３０は、外輪１５の形状が、第１実施形態と異なり、他の部位は同様に構成される。
【００２２】
第２実施形態の複列円すいころ軸受３０に用いられる外輪３１には、フランジ３２が形成されている。フランジ３２は、遊星歯車式自動変速機の遊星歯車機構におけるハウジングに対して、ねじ止めや嵌着される際に用いられる。
第２実施形態の複列円すいころ軸受３０は、第１実施形態と同様の作用・効果を有するため、記述は省略する。
【００２３】
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く、適宜な変形、改良等が可能である。
例えば、複列のうちの他方の列における潤滑油の必要量を、一方の列における潤滑油の必要量よりも多く設定する組付環境に対しては、内輪の突き合わせ面を、他方の列に配される他方の保持器と一方の列に配される一方の保持器との中間位置より他方の列の内輪における軸受端面側に配置すれば良い。
また、油溝から供給される潤滑油としては、耐荷重性能が高く酸化安定性が良く、防錆性能の良い高度精製鉱油又は合成油が好ましく、リチウム系グリース等のグリースや潤滑剤ポリマー部材等を適宜選択して用いるのが良い。
また、油溝の形状については、突き合わせ面においてＶ字状の溝形状をなすものに代えて、Ｕ字状の溝形状やコ字状の溝形状にしても良い。
【００２４】
【発明の効果】
以上説明したように、本発明の複列円すいころ軸受によれば、両保持器の中間位置より軸受端面側にオフセットした位置に一対の内輪の突き合わせ面が配される。
したがって、複列のうちの一方の列における潤滑油の必要量を、他方の列における潤滑油の必要量よりも多く設定する組付環境に対しては、内輪の突き合わせ面を、一方の列に配される一方の保持器と他方の列に配される他方の保持器との中間位置より一方の列の内輪における軸受端面側に配置することにより、油溝を通じて供給される潤滑油が一方の保持器で受け取られ、一方の列の軸受空間にのみ集中して供給されて一方の列を積極的に潤滑する。また、他方の列に対しては、一方の列に供給されない潤滑油が供給される。これにより、潤滑油をいずれか一方の列に積極的に供給することにより組み付けられる環境に対応して優れた潤滑性能を有する複列円すいころ軸受を提供することができる。
【図面の簡単な説明】
【図１】本発明の複列円すいころ軸受の第１実施形態を示す半断面図である。
【図２】本発明の複列円すいころ軸受の第２実施形態を示す半断面図である。
【図３】従来の複列円すいころ軸受を示す断面図である。
【符号の説明】
１０，３０ 複列円すいころ軸受
１１，１２ 内輪
１１ａ 軸受端面
１３，１４ 内輪軌道面
１５ 外輪
１６，１７ 外輪軌道面
１８ 円すいころ（転動体）
１９，２０ 保持器
２２ 突き合わせ面
２３ 油溝[0001]
BACKGROUND OF THE INVENTION
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double-row tapered roller bearing used to support a ring gear of an automatic transmission for an automobile, for example, so as to be rotatable with respect to a rotating shaft, and more particularly to a double-row tapered roller having an oil groove for supplying lubricating oil. Related to bearings.
[0002]
[Prior art]
As the double row tapered roller bearing described above, a double row tapered roller bearing 50 shown in FIG. 3 includes an outer ring 51 having double row outer ring raceways 52 and 52, inner rings 53 and 53 having inner ring raceways 54 and 54, rolling elements 55, In the planetary gear mechanism of the planetary gear type automatic transmission, the cage 56 is disposed between the rotating shaft 57 and a housing 58 disposed on the outer peripheral surface of the intermediate portion of the rotating shaft 57. In the double row tapered roller bearing 50, a concave groove 59 is provided in the circumferential direction between the outer ring raceways 52, 52 on the inner circumferential surface in the axial direction intermediate portion of the outer ring 51. The concave groove 59 temporarily stores the lubricating oil discharged from the notches 60 and 60 formed in the butted end surfaces of the inner rings 53 and 53.
[0003]
Such a double-row tapered roller bearing 50 widely spreads the lubricating oil discharged from the portion between the inner ring raceways 54, 54 at the axially intermediate portion of the inner rings 53, 53 through the notches 60, 60 in the circumferential direction. By distributing, the lubricating oil discharged from the outer peripheral surface of the rotary shaft 57 flows through the notches 60, 60 from the inner side in the diametrical direction to the surroundings due to the centrifugal force accompanying the rotation, and a part of them is scattered. It is collected in the concave groove 59 (see, for example, Patent Document 1).
[0004]
[Patent Document 1]
Japanese Patent Laid-Open No. 10-274243 (page 4-5, FIG. 1)
[0005]
[Problems to be solved by the invention]
However, in the double-row tapered roller bearing 50 described in Patent Document 1, the butted end surface portions of the inner rings 53 and 53 are disposed in the middle of the two cages 56 and 56, and the butted end surface portions of the inner rings 53 and 53 are arranged. Lubricating oil discharged from the notches 60, 60 formed in is distributed widely over the circumferential direction. However, in an environment where a double-row tapered roller bearing is actually used, the required amount of lubricating oil in each row is different. In the double-row tapered roller bearing 50 described above, either one of the lubricating oils is used depending on the required amount. It is difficult to sort them into columns.
[0006]
The present invention has been made in view of the above problems, and by actively supplying lubricating oil to one of the rows, a double row tapered roller bearing having excellent lubrication performance in accordance with the assembled environment The purpose is to provide.
[0007]
[Means for Solving the Problems]
The double-row tapered roller bearing according to claim 1 of the present invention is provided with a pair of inner rings each having an inner ring raceway surface, an outer ring having an outer ring raceway surface, and a relatively rotatable arrangement between the inner ring raceway surface and the outer ring raceway surface. A double row tapered roller bearing having a plurality of rolling elements and a pair of cages for holding the rolling elements in a freely rolling manner, and having an oil groove for supplying lubricating oil on the abutting surfaces of the pair of inner rings The oil groove for supplying the lubricating oil is offset toward the bearing end surface from the intermediate position of the two cages, and is arranged on the pocket side from one small-diameter ring portion of the pair of cages in the axial direction. Thus, the required amount of lubricating oil in one row of the double rows is set to be larger than the required amount of lubricating oil in the other row .
[0008]
According to the double-row tapered roller bearing having the above-described configuration, the butted surfaces of the pair of inner rings are arranged at a position offset from the intermediate position between the two cages toward the bearing end surface.
Therefore, for an assembly environment in which the required amount of lubricating oil in one of the double rows is set to be greater than the required amount of lubricating oil in the other row, the butt surface of the inner ring is placed in one row. By arranging the retainer on the bearing end surface side of the inner ring in one row from the intermediate position between the one retainer arranged in the other row and the other retainer arranged in the other row, the lubricating oil supplied through the oil groove is It will be received by the cage and will be supplied in a concentrated manner only in the bearing space of one row, actively lubricating one row. Further, the lubricating oil that has not been supplied to one row is supplied to the other row. Thereby, lubricating oil can be positively supplied to any one row | line, and the double row tapered roller bearing which has the outstanding lubrication performance according to the assembly | attachment environment can be provided.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of the double row tapered roller bearing of the present invention will be described in detail with reference to FIGS.
[0010]
FIG. 1 is a half sectional view showing a first embodiment of a double row tapered roller bearing according to the present invention, and FIG. 2 is a half sectional view showing a second embodiment of the double row tapered roller bearing according to the present invention. Note that in the second embodiment, members and the like having the same configurations and functions as those already described are denoted by the same or corresponding reference numerals in the drawing, and the description thereof is simplified or omitted.
[0011]
As shown in FIG. 1, the double row tapered roller bearing 10 of the first embodiment includes an inner ring 11, 12 having inner ring raceway surfaces 13, 14, an outer ring 15 having outer ring raceway surfaces 16, 17, and an inner ring raceway surface 13. A plurality of tapered rollers 18 that are relatively rotatably disposed between the outer ring raceway surface 16 and the outer ring raceway surface 14 and the outer ring raceway surface 17, and a pair of cages 19 that hold the tapered rollers 18 in a rollable manner. 20. In this double row tapered roller bearing 10, the inner rings 11, 12 are back to back.
[0012]
Among the inner rings 11, 12, the inner ring 12 disposed on the left side in FIG. 1 is directed toward the inner ring 11 disposed on the right side in FIG. 1 on the outer peripheral surface on which the inner ring raceway surface 14 is formed. An extended portion 21 that extends is formed. Therefore, the inner ring 12 has an axial length L1 that is longer than an axial length L2 of the inner ring 11. That is, the abutting surface 22 between the inner ring 11 and the inner ring 12 is disposed offset from the intermediate position of the inner ring raceway surfaces 13 and 14 (or the outer ring raceway surfaces 16 and 17) toward the bearing end surface.
[0013]
An oil groove 23 is formed at the end of the inner ring 11 and the inner ring 12 on the abutting surface 22 side. The oil groove 23 is arranged in the circumferential direction corresponding to the abutting surface 22. The oil groove 23 is formed on the abutting surface 22 of the inner ring 11 having the axial length L2 and the inner ring 12 having the axial length L1, and is closer to the end surface 11a side of the one inner ring 11 with respect to the bearing center line a1. Are arranged. These inner rings 11 and 12 are fitted with a rotation shaft in a planetary gear mechanism of a planetary gear type automatic transmission. Here, the oil groove 23 has a V-shaped groove shape on the abutting surface 22.
[0014]
The outer ring 15 has one outer ring raceway surface 16 arranged in one row and the other outer ring raceway surface 17 arranged in the other row. The outer ring 15 is fitted in the housing of the planetary gear mechanism of the planetary gear type automatic transmission.
[0015]
The inner ring raceways 13 and 14 of the inner rings 11 and 12, the outer ring raceway surfaces 16 and 17 of the outer ring 15, and the tapered rollers 18 are set so that the apexes on the extension of the respective conical surfaces converge at one point on the axis. Has been. The inner ring raceways 13 and 14 of the inner rings 11 and 12 restrict the movement of the tapered rollers 18 in the axial direction.
[0016]
The cages 19 and 20 are steel plate cage press cages, and are punched in correspondence with the shape of the tapered roller 18 between the large-diameter ring portions 19a and 20a and the small-diameter ring portions 19b and 20b. A plurality of isosceles trapezoidal pockets 19c, 20c are arranged in the circumferential direction. Since the cages 19 and 20 are arranged to face each other across the bearing center line a1 that coincides with the intermediate position, one cage 19 is arranged corresponding to one outer ring raceway surface 16 of the outer ring 15, The other cage 20 is arranged corresponding to the other outer ring raceway surface 17. The inner peripheral portions of the cages 19 and 20 are fixed to the outer peripheral surface of the other inner ring 12 by caulking.
[0017]
Since one cage 19 is arranged corresponding to one outer ring raceway surface 16 of the outer ring 15 and the other cage 20 is arranged corresponding to the other outer ring raceway surface 17, one cage is arranged. 19 functions to positively receive the lubricating oil supplied from the oil groove 23 disposed closer to the end surface 11a side of the one inner ring 11 with respect to the bearing center line a1.
[0018]
The double-row tapered roller bearing 10 described above is assembled to the planetary gear mechanism of the planetary gear type automatic transmission by the inner shafts 11 and 12 having the main shaft fitted therein and the outer ring 15 fitted in the housing. When the main shaft is rotated by operating the planetary gear type automatic transmission, the lubricating oil is supplied from the external lubricating oil supply means to the oil groove 23, and the lubricating oil flows out from the oil groove 23 into the bearing space. At that time, the lubricating oil flows from the oil groove 23 toward the outer periphery of the bearing by the centrifugal force and the feeding pressure due to the rotation of the inner rings 11 and 12, and the flowing lubricating oil collides with one of the cages 19. The lubricating oil colliding with one of the cages 19 is supported by one outer ring raceway surface 16 of the outer ring 15, the inner ring raceway surface 13 of one inner ring 11, the outer ring raceway surface 16 and the inner ring raceway surface 13. A large amount is supplied to one row of rollers 18.
[0019]
At the same time, the remaining lubricating oil that did not collide with one of the cages 19 is supported by the other outer ring raceway surface 17 of the outer ring 15, the inner ring raceway surface 14 of the other inner ring 12, the outer ring raceway surface 17, and the inner ring raceway surface 14. Is supplied to the other row of tapered rollers 18. That is, the lubricating oil is distributed according to the assembly environment in which the required amount of lubricating oil in one row of the double rows is set to be larger than the required amount of lubricating oil in the other row.
[0020]
As described above, according to the double-row tapered roller bearing 10 of the first embodiment, the pair of inner rings 11, 12 is located at a position offset toward the bearing end surface 11 a side from the bearing center line a 1 that coincides with the intermediate position between the two cages 19, 20. A butting surface 22 is arranged.
Therefore, for the assembly environment in which the required amount of lubricating oil in one row of the double rows is set to be larger than the required amount of lubricating oil in the other row, the abutting surfaces 22 of the inner rings 11, 12 are By disposing the retainer 19 arranged in one row and the other retainer 20 arranged in the other row on the bearing end surface 11a side of the inner ring 11 in one row, the oil groove 23 is arranged. The lubricating oil supplied through is received by one of the cages 19 and supplied concentratedly only in the bearing space of one row to actively lubricate one row. In addition, lubricating oil that is not supplied to one row is supplied to the other row. Thereby, the double row tapered roller bearing 10 which has the outstanding lubrication performance corresponding to the environment assembled | attached by supplying lubricating oil to any one row actively can be provided.
[0021]
Next, a second embodiment according to the present invention will be described with reference to FIG.
As shown in FIG. 2, the double-row tapered roller bearing 30 according to the second embodiment differs from the first embodiment in the shape of the outer ring 15, and other parts are configured in the same manner.
[0022]
A flange 32 is formed on the outer ring 31 used in the double-row tapered roller bearing 30 of the second embodiment. The flange 32 is used when screwing or fitting to the housing in the planetary gear mechanism of the planetary gear type automatic transmission.
Since the double row tapered roller bearing 30 of the second embodiment has the same operations and effects as those of the first embodiment, description thereof is omitted.
[0023]
In addition, this invention is not limited to embodiment mentioned above, A suitable deformation | transformation, improvement, etc. are possible.
For example, for an assembly environment where the required amount of lubricating oil in the other row of the multiple rows is set to be greater than the required amount of lubricating oil in one row, the butt surface of the inner ring is placed in the other row. What is necessary is just to arrange | position to the bearing end surface side in the inner ring | wheel of the other row | line | column from the intermediate position of the other cage | basket | distributor arrange | positioned and one cage | basket arranged in one row | line.
Also, as the lubricating oil supplied from the oil groove, highly refined mineral oil or synthetic oil with high load bearing performance, good oxidation stability and good rust prevention performance is preferable, such as grease such as lithium grease, lubricant polymer member, etc. Is preferably selected and used.
Further, the shape of the oil groove may be a U-shaped groove shape or a U-shaped groove shape instead of a V-shaped groove shape on the abutting surface.
[0024]
【The invention's effect】
As described above, according to the double row tapered roller bearing of the present invention, the butted surfaces of the pair of inner rings are arranged at a position offset from the intermediate position between the two cages toward the bearing end face.
Therefore, for an assembly environment in which the required amount of lubricating oil in one of the double rows is set to be greater than the required amount of lubricating oil in the other row, the butt surface of the inner ring is placed in one row. By arranging the retainer on the bearing end surface side of the inner ring in one row from the intermediate position between the one retainer arranged in the other row and the other retainer arranged in the other row, the lubricating oil supplied through the oil groove is It is received by the cage and supplied in a concentrated manner only in the bearing space of one row to actively lubricate one row. In addition, lubricating oil that is not supplied to one row is supplied to the other row. As a result, it is possible to provide a double-row tapered roller bearing having excellent lubricating performance corresponding to the environment in which the lubricating oil is positively supplied to one of the rows.
[Brief description of the drawings]
FIG. 1 is a half sectional view showing a first embodiment of a double row tapered roller bearing of the present invention.
FIG. 2 is a half sectional view showing a second embodiment of the double-row tapered roller bearing of the present invention.
FIG. 3 is a cross-sectional view showing a conventional double row tapered roller bearing.
[Explanation of symbols]
10, 30 Double-row tapered roller bearings 11, 12 Inner ring 11a Bearing end faces 13, 14 Inner ring raceway surface 15 Outer rings 16, 17 Outer ring raceway surface 18 Tapered rollers (rolling elements)
19, 20 Cage 22 Butting surface 23 Oil groove

Claims (1)

それぞれ内輪軌道面を有する一対の内輪と、外輪軌道面を有する外輪と、前記内輪軌道面及び前記外輪軌道面間に相対回転自在に配された複数の転動体と、前記転動体を転動自在に保持する一対の保持器と、を有し、前記一対の内輪の突き合わせ面に潤滑油供給用の油溝を有する複列円すいころ軸受であって、
前記潤滑油供給用の油溝が、前記両保持器の中間位置より軸受端面側にオフセットして、軸方向において前記一対の保持器の一方の小径リング部よりポケット側に配され、これにより、複列のうちの一方の列における潤滑油の必要量を、他方の列における潤滑油の必要量よりも多く設定することを特徴とする複列円すいころ軸受。A pair of inner rings each having an inner ring raceway surface, an outer ring having an outer ring raceway surface, a plurality of rolling elements arranged to be relatively rotatable between the inner ring raceway surface and the outer ring raceway surface, and the rolling elements are rotatable. A double row tapered roller bearing having a lubricating oil supply oil groove on the abutting surfaces of the pair of inner rings,
The oil groove for supplying the lubricating oil is offset toward the bearing end surface from the intermediate position of the two cages, and is arranged on the pocket side from one small-diameter ring portion of the pair of cages in the axial direction . A double row tapered roller bearing, wherein the required amount of lubricating oil in one of the double rows is set to be larger than the required amount of lubricating oil in the other row .
JP2003101606A 2003-04-04 2003-04-04 Double row tapered roller bearing Expired - Fee Related JP4321092B2 (en)

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