JP5012438B2 - Needle roller bearing - Google Patents

Needle roller bearing Download PDF

Info

Publication number
JP5012438B2
JP5012438B2 JP2007292329A JP2007292329A JP5012438B2 JP 5012438 B2 JP5012438 B2 JP 5012438B2 JP 2007292329 A JP2007292329 A JP 2007292329A JP 2007292329 A JP2007292329 A JP 2007292329A JP 5012438 B2 JP5012438 B2 JP 5012438B2
Authority
JP
Japan
Prior art keywords
needle roller
roller bearing
portions
pair
planetary gear
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
JP2007292329A
Other languages
Japanese (ja)
Other versions
JP2009115300A5 (en
JP2009115300A (en
Inventor
文 菊池
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 JP2007292329A priority Critical patent/JP5012438B2/en
Publication of JP2009115300A publication Critical patent/JP2009115300A/en
Publication of JP2009115300A5 publication Critical patent/JP2009115300A5/ja
Application granted granted Critical
Publication of JP5012438B2 publication Critical patent/JP5012438B2/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
    • F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
    • F16C33/546—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part with a M- or W-shaped cross section
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/541—Details of individual pockets, e.g. shape or roller retaining means
    • 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
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • F16C19/463—Needle bearings with one row or needles consisting of needle rollers held in a cage, i.e. subunit without race 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Abstract

<P>PROBLEM TO BE SOLVED: To provide a needle roller bearing capable of efficiently holding lubricating oil on a rolling surface by a limited lubricating oil quantity, without impairing retentivity to a needle-like roller. <P>SOLUTION: This needle roller bearing 10 is composed of a pair of annular parts 13 and a plurality of column parts 14 connecting the annular parts 13, and has a cage 11 forming a plurality of pockets 15 and a plurality of needle-like rollers 12 rollingly held by the pockets 15, and is formed by arranging a narrow width part 17 narrowing in width in the peripheral direction in the middle of the column parts 14. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

本発明は、例えば、自動車、自動２輪車、航空機、鉄道、電気・情報、鉄鋼等の産業用の分野における遊星歯車機構等において遊星歯車の支持に用いられる針状ころ軸受に関する。   The present invention relates to a needle roller bearing used for supporting planetary gears in planetary gear mechanisms and the like in industrial fields such as automobiles, motorcycles, aircraft, railways, electricity / information, and steel.

遊星歯車機構は、キャリアに支持されているピニオンシャフトに、針状ころ軸受を介して複数の遊星歯車が組み付けられており、遊星歯車が、リングギアの内歯と、太陽ギアの外歯と、に噛合されて構成されている。   In the planetary gear mechanism, a plurality of planetary gears are assembled to pinion shafts supported by a carrier via needle roller bearings, and the planetary gears include ring gear internal teeth, sun gear external teeth, It is configured to be engaged with each other.

ここで、自動車用の自動変速機に使用される遊星歯車機構においては、遊星歯車が自転しながら、キャリアを伴って公転する複雑な構造のために、潤滑油が十分に行きわたらない嫌いがある。   Here, in the planetary gear mechanism used in the automatic transmission for automobiles, the planetary gear rotates and revolves with the carrier, so that there is a dislike that the lubricating oil is not sufficiently distributed. .

そして、近年、自動車における燃費の向上ため、小型化が要求されており、そのため遊星歯車の回転速度が高速になる等、遊星歯車機構全体の使用条件が厳しくなってきている。これに伴い、潤滑の改善が一層要求されている状況にあり、その潤滑の改善を図るため、供給油量を増加させるか、ピニオンシャフトの油孔の数を増やすか、或いは、ピニオンシャフトの油孔径を大きくするか、等がまず考えられる。しかし、このように潤滑油の供給量を単純に増加したとしても、実際に針状ころ軸受に到達する油量を、それに比例して増加させることは難しい。   In recent years, miniaturization has been demanded in order to improve fuel efficiency in automobiles, and as a result, the use conditions of the planetary gear mechanism as a whole have become severe, such as the rotational speed of the planetary gear being increased. Along with this, there is a further demand for improved lubrication, and in order to improve the lubrication, the amount of oil supplied is increased, the number of oil holes in the pinion shaft is increased, or the oil of the pinion shaft is increased. The first possibility is to increase the hole diameter. However, even if the supply amount of the lubricating oil is simply increased in this way, it is difficult to increase the amount of oil that actually reaches the needle roller bearing in proportion thereto.

また、針状ころ軸受における転がり疲れ寿命（軸受の回転運動に伴って、転がり面に受ける繰り返し剪断応力により転動部品が疲労し、その表面の一部に剥離が生ずるまの総回転数）を長くするために、転動面へ潤滑油を十分に供給して油膜を保持することが要求されている。   In addition, the rolling fatigue life of needle roller bearings (the total number of revolutions until the rolling parts become fatigued due to repeated shear stress applied to the rolling surface as the bearing rotates and the surface partly peels) In order to increase the length, it is required to sufficiently supply lubricating oil to the rolling surface to hold the oil film.

その対策として、図４に示すように、保持器７１のポケット７２のコーナー部７３に、ぬすみ部７４を設けた針状ころ軸受７０が知られている（例えば、特許文献１参照）。   As a countermeasure, as shown in FIG. 4, a needle roller bearing 70 is known in which a corner portion 73 of a pocket 72 of a cage 71 is provided with a relief portion 74 (see, for example, Patent Document 1).

この特許文献１に開示された針状ころ軸受７０は、ぬすみ部７４の深さを、針状ころ７５の直径に対する所定の値とすることで、ぬすみ部７４を潤滑油の流通路として、保持器７１の内径側と外径側との間で、潤滑油をスムーズに行きわたらせようとしているものである。   The needle roller bearing 70 disclosed in this patent document 1 holds the thin portion 74 as a lubricating oil flow passage by setting the depth of the thin portion 74 to a predetermined value with respect to the diameter of the needle roller 75. The lubricating oil is to be spread smoothly between the inner diameter side and the outer diameter side of the vessel 71.

また、図５に示すように、針状ころ８１を保持する保持器８２の柱部８３の中央部の肉厚を、他の部分よりも薄くした針状ころ軸受８０が提案されている（例えば、特許文献２参照）。   Further, as shown in FIG. 5, a needle roller bearing 80 is proposed in which the thickness of the central portion of the column portion 83 of the retainer 82 that holds the needle rollers 81 is thinner than other portions (for example, , See Patent Document 2).

この特許文献２に開示された針状ころ軸受８０は、柱部８３の中央部である縮径部８４の肉厚ｔ１を、それ以外の部位である、案内面８５の肉厚ｔ２および環状部８６のフランジ部の肉厚ｔ３未満或いは以下にすることで軽量化を図ろうとしているものである。   In the needle roller bearing 80 disclosed in Patent Document 2, the thickness t1 of the reduced diameter portion 84, which is the center portion of the column portion 83, is changed from the thickness t2 of the guide surface 85, which is the other portion, and the annular portion. By reducing the thickness of the flange portion 86 to less than or less than 86, the weight is reduced.

特開平１１−１０８０６５号公報Japanese Patent Laid-Open No. 11-108065 特開２００４−３５３８０９号公報JP 2004-353809 A

しかしながら、上記特許文献１に開示された従来の針状ころ軸受７０においては、保持器７１の柱部の幅が応力の集中しやすいポケット７２のコーナー部７３で細くなっているため、運転中に保持器７１の破損等が起きてしまい、針状ころが脱落する等の不具合が生じてしまう虞がある。   However, in the conventional needle roller bearing 70 disclosed in Patent Document 1, the width of the column portion of the retainer 71 is narrowed at the corner portion 73 of the pocket 72 where stress tends to concentrate. There is a risk that the retainer 71 may be damaged, causing problems such as dropping of the needle rollers.

また、上記特許文献２に開示された従来の針状ころ軸受８０においては、保持器８２の柱部８３の角部分と針状ころ８１との接触において、針状ころ８１の保持性が確実でない虞があるとともに、潤滑油の流通性を改善する余地がある。   Further, in the conventional needle roller bearing 80 disclosed in Patent Document 2, the retainability of the needle roller 81 is not reliable in the contact between the corner portion of the column portion 83 of the cage 82 and the needle roller 81. There is a concern and there is room for improving the flowability of the lubricating oil.

本発明は、前述した事情に鑑みてなされたものであり、その目的は、針状ころに対する保持性を損なうことなく、且つ限られた潤滑油量で転動面での潤滑油を効率的に保持することができる針状ころ軸受を提供することにある。   The present invention has been made in view of the above-described circumstances, and an object of the present invention is to efficiently remove lubricating oil on the rolling surface with a limited amount of lubricating oil without impairing the retainability to the needle rollers. It is providing the needle roller bearing which can be hold | maintained.

前述した本発明の目的は、下記の構成により達成される。   The object of the present invention described above is achieved by the following configuration.

（１）軸方向に互いに間隔をあけて配置された一対の環状部と、円周方向に亙って間欠的に配置されて前記一対の環状部を連結する複数の柱部と、を有して、前記環状部と前記柱部と間に複数のポケットが形成された保持器と、前記ポケットに転動自在に保持された複数の針状ころと、を備えた針状ころ軸受であって、前記柱部は、前記一対の環状部の周縁からそれぞれ軸方向内方に延出して軸方向両端部にそれぞれ位置する一対の端板部と、軸方向中間に位置し径方向内方に縮径されて前記一対の端板部よりも径方向内方に配設される中央板部と、前記一対の端板部の軸方向内方の端部と前記中央板部の軸方向両端部とを軸方向に対して傾斜した状態で連結する一対の斜板部と、を有し、前記中央板部の中間に、周方向に向けて幅狭となる幅狭部が設けられ、前記ポケットの軸方向長さをＬ１、前記中央板部の軸方向長さ寸法をＬ２、前記幅狭部の軸方向長さをＬ３、前記中央板部の周方向幅寸法をＬ４、前記幅狭部の周方向幅寸法をＬ５とするとき、Ｌ１＞Ｌ２＞Ｌ３、且つＬ４＞Ｌ５となるように設けられ、これにより、前記中央板部の中間部分で、前記保持器と前記針状ころの転動面との間に潤滑油の流路となる隙間が形成されることを特徴とする針状ころ軸受。
（２）前記幅狭部の周方向縁部は面取り加工が施されることを特徴とする（１）に記載の針状ころ軸受。
（３）ピニオンシャフトの両端をキャリアで支持した遊星歯車機構における遊星歯車の支持に用いられる（１）又は（２）に記載の針状ころ軸受。 (1) It has a pair of annular parts arranged at intervals in the axial direction, and a plurality of column parts intermittently arranged in the circumferential direction to connect the pair of annular parts. A needle roller bearing comprising: a cage in which a plurality of pockets are formed between the annular portion and the column portion; and a plurality of needle rollers that are rotatably held in the pockets. The column portions extend inward in the axial direction from the peripheral edges of the pair of annular portions, respectively, and a pair of end plate portions positioned at both axial end portions, respectively, and are positioned in the axial direction and radially contracted inward. A central plate portion that is radially arranged and arranged radially inward of the pair of end plate portions, an axially inner end portion of the pair of end plate portions, and both axial end portions of the central plate portion the has a pair of swash plate portion connecting in a state tilted with respect to the axial direction, and in the middle of the central plate portion, the narrower toward the circumferential direction Narrow portion is provided, the axial length of the pocket L1, the axial length of the central plate portion L2, the axial length of the narrow section L3, the circumferential width dimension of the central plate portion Is L4, and when the circumferential width dimension of the narrow portion is L5, L1>L2> L3 and L4> L5 are provided. And a rolling surface of the needle roller, a gap serving as a flow path for the lubricating oil is formed .
(2) The needle roller bearing according to (1), wherein a circumferential edge of the narrow portion is chamfered.
( 3 ) The needle roller bearing according to (1) or (2) , which is used for supporting a planetary gear in a planetary gear mechanism in which both ends of a pinion shaft are supported by a carrier.

上記（１）に記載の構成によれば、柱部の中間位置において周方向に幅狭の幅狭部を通じて保持器の外径側および内径側からの潤滑油の流路が形成される。これにより、限られた潤滑油量で転動面での潤滑油を効率的に保持することができる。また、柱部の中間において容量が減少されることで、回転時の遠心力が負荷されたとしても、柱部は自重に伴う変形が抑制されて、針状ころに対する保持性を損なうことがない。
また、上記（２）に記載の構成によれば、幅狭部の周方向縁部は面取り加工が施されることにより、針状ころとの接触、及び潤滑油の流動性などを考慮することができる。
そして、上記（３）に記載の構成によれば、ピニオンシャフトの軸心を通過して油孔から流出してきた潤滑油は、針状ころとピニオンシャフトとの転動面を通過して遊星歯車の自転による遠心力で保持器の外径側に押し出される。その際、ピニオンシャフトと柱部とが最も接近する柱部の中間において幅が狭くなっている幅狭部を有しているので、柱部と針状ころとの間に隙間が確保され、その隙間を通じて潤滑油が保持器の外径側へ効率よく流動される。このため、複雑な機構で潤滑油が十分に行きわたらないとされる遊星歯車機構においても、限られた潤滑油量で転動面での潤滑油を効率的に保持することができる。さらに、幅狭部は、撓み量が最大となる柱部の中間部における容量を減少させるために、遊星歯車の公転および自転による遠心力が負荷されたとしても、柱部は自重に伴う変形が抑制されることで、コーナー部への応力集中が低減されて、針状ころに対する保持性を損なうことがない。 According to the configuration described in the above (1), the flow path of the lubricating oil from the outer diameter side and the inner diameter side of the cage is formed through the narrow portion narrow in the circumferential direction at the intermediate position of the column portion. Thereby, the lubricating oil on the rolling surface can be efficiently held with a limited amount of lubricating oil. In addition, since the capacity is reduced in the middle of the column part, even if a centrifugal force is applied during rotation, the column part is prevented from being deformed due to its own weight and does not impair the retainability to the needle rollers. .
Further, according to the configuration described in (2) above, the circumferential edge of the narrow portion is chamfered so that contact with the needle rollers and fluidity of the lubricating oil are taken into consideration. Can do.
And according to the structure as described in said ( 3 ), the lubricating oil which flowed out from the oil hole through the shaft center of a pinion shaft passes the rolling surface of a needle roller and a pinion shaft, and it is a planetary gear. It is pushed out to the outer diameter side of the cage by the centrifugal force due to the rotation of. At that time, since the pinion shaft and the column part have a narrow part that is narrow in the middle of the column part that is closest, a gap is secured between the column part and the needle roller, Lubricating oil efficiently flows to the outer diameter side of the cage through the gap. For this reason, even in the planetary gear mechanism in which the lubricating oil is not sufficiently distributed by a complicated mechanism, the lubricating oil on the rolling surface can be efficiently held with a limited amount of lubricating oil. Furthermore, in order to reduce the capacity of the intermediate portion of the column portion where the amount of bending is maximum, the narrow portion is deformed due to its own weight even if the centrifugal force due to the revolution and rotation of the planetary gear is applied. By being suppressed, the stress concentration on the corner portion is reduced, and the retainability with respect to the needle rollers is not impaired.

本発明によれば針状ころに対する保持性を損なうことなく、且つ限られた潤滑油量で転動面での潤滑油を効率的に保持することができる針状ころ軸受を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the needle roller bearing which can hold | maintain the lubricating oil on a rolling surface efficiently with the limited amount of lubricating oil can be provided, without impairing the retainability with respect to a needle roller. .

以下、本発明に係る好適な実施形態について、図面を参照しながら説明する。
なお、図１〜３は本発明に係る針状ころ軸受の一実施形態を示すものあり、図１は本発明の一実施形態に係る針状ころ軸受の外観斜視図であり、図２は図１の針状ころ軸受の一部破断側面図であり、図３は図１の針状ころ軸受を適用した遊星歯車機構の分解斜視図である。 Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
1 to 3 show an embodiment of a needle roller bearing according to the present invention, FIG. 1 is an external perspective view of the needle roller bearing according to an embodiment of the present invention, and FIG. 1 is a partially broken side view of the needle roller bearing 1 and FIG. 3 is an exploded perspective view of a planetary gear mechanism to which the needle roller bearing of FIG. 1 is applied.

図１に示すように、本発明の一実施形態の針状ころ軸受１０は、保持器１１と、複数の針状ころ１２と、を備えて構成される。
なお、本実施形態では後述する遊星歯車機構に用いられるため内輪相当部材及び外輪相当部材を直接備えた構成となっていないが、種々の外輪相当部材又は内輪相当部材の少なくとも１つを備えた針状ころ軸受に対しても本発明を適宜適用することができる。 As shown in FIG. 1, a needle roller bearing 10 according to an embodiment of the present invention includes a cage 11 and a plurality of needle rollers 12.
In this embodiment, since it is used for a planetary gear mechanism described later, it does not have a structure directly provided with an inner ring equivalent member and an outer ring equivalent member, but a needle provided with at least one of various outer ring equivalent members or inner ring equivalent members. The present invention can be appropriately applied to a tapered roller bearing.

保持器１１は、例えば機械構造用鋼材等の金属製板部材に対し打ち抜き加工及び曲げ加工などを施すことで、軸方向に互いに間隔をあけて配置された一対の環状部１３と、円周方向に亙って間欠的に配置されて前記一対の環状部１３を連結する複数の柱部１４と、を有して成形されて、一対の環状部１３と柱部１４との間にポケット１５がそれぞれ周方向に等間隔に形成される。   The cage 11 is formed by punching and bending a metal plate member such as a steel material for machine structure, for example, and a pair of annular portions 13 that are spaced apart from each other in the axial direction, and a circumferential direction. And a plurality of column portions 14 that are intermittently arranged to connect the pair of annular portions 13, and are formed with a pocket 15 between the pair of annular portions 13 and the column portions 14. Each is formed at equal intervals in the circumferential direction.

柱部１４は、軸方向の中間に配置された中央板部１６が、段部形状で内周部に向けて縮径されることで、針状ころ１２の抜け止めとして機能し、そしてこの中央板部１６の中間位置に後述する幅狭部１７が形成されている。 The column portion 14 functions as a stopper for the needle rollers 12 by the central plate portion 16 disposed in the middle in the axial direction being reduced in diameter toward the inner peripheral portion in a stepped shape, and this center A narrow portion 17 described later is formed at an intermediate position of the plate portion 16.

針状ころ１２は、丸棒形状に形成されており、また焼入れ後に、研削仕上げが施された後適切なクラウニング処理が施されるため、両端部での応力集中を緩和することができる。   Since the needle roller 12 is formed in a round bar shape, and after quenching, an appropriate crowning process is performed after the grinding finish, so that stress concentration at both ends can be reduced.

図２に示すように、保持器１１において、ポケット１５は長さ寸法Ｌ１の軸方向長さを有し、そして中央板部１６が長さ寸法Ｌ２の軸方向長さを有するとともに幅狭部１７が長さ寸法Ｌ３の軸方向長さを有しており、これら長さの関係は、Ｌ１＞Ｌ２＞Ｌ３とされる。   As shown in FIG. 2, in the retainer 11, the pocket 15 has an axial length of the length dimension L1, and the central plate portion 16 has an axial length of the length dimension L2 and the narrow portion 17. Has a length in the axial direction of the length dimension L3, and the relationship between these lengths is L1> L2> L3.

ここで、中央板部１６の周方向両端部に凹部が形成され、このため、中央板部１６が周方向に幅寸法Ｌ４を有しているとき、幅狭部１７は周方向にこの幅寸法Ｌ４よりも狭い幅寸法Ｌ５とされて形成される（即ち、Ｌ４＞Ｌ５）。
したがって、幅狭部１７により、中央板部１６の中間部分で、保持器１１と針状ころ１２の転動面との間に隙間が形成されて、潤滑油の流路が形成されることとなる。
なお、針状ころ１２との接触、及び潤滑油の流動性などを考慮して、幅狭部１７の周方向縁部は面取り加工が施され、また幅狭部１７の軸方向端部の周面を比較的滑らかな曲線を有する連続面とするのが好適である。 Here, concave portions are formed at both ends in the circumferential direction of the central plate portion 16, and therefore when the central plate portion 16 has a width dimension L4 in the circumferential direction, the narrow portion 17 has this width dimension in the circumferential direction. The width L5 is narrower than L4 (ie, L4> L5).
Therefore, the narrow portion 17 forms a gap between the retainer 11 and the rolling surface of the needle roller 12 at the intermediate portion of the central plate portion 16, thereby forming a lubricating oil flow path. Become.
In consideration of the contact with the needle roller 12 and the fluidity of the lubricating oil, the circumferential edge of the narrow portion 17 is chamfered, and the periphery of the axial end portion of the narrow portion 17 is also provided. The surface is preferably a continuous surface having a relatively smooth curve.

そして、図３に示すように、このように構成された針状ころ軸受１０は、遊星歯車機構３０において、３個の遊星歯車３１にそれぞれ組付けられる。
遊星歯車機構３０は、内歯３３を有するリングギア３２と、外歯３５を有する太陽ギア３４と、リングギア３２の内歯３３および太陽ギア３４の外歯３５に噛合する遊星歯車３１と、不図示の油孔を有するとともに、遊星歯車３１をそれぞれ支持する３本のピニオンシャフト３６と、ピニオンシャフト３６の両端を支持していて遊星歯車３１を回転自在に支持するとともに自らも回転可能なキャリア３７と、を備える。針状ころ軸受１０は、ピニオンシャフト３６に外嵌され、遊星歯車３１に保持器１１が外径支持で取付けられて、軸受空間に所定の潤滑油が充填される。 As shown in FIG. 3, the needle roller bearing 10 configured in this way is assembled to each of the three planetary gears 31 in the planetary gear mechanism 30.
The planetary gear mechanism 30 includes a ring gear 32 having inner teeth 33, a sun gear 34 having outer teeth 35, a planetary gear 31 meshing with the inner teeth 33 of the ring gear 32 and the outer teeth 35 of the sun gear 34, and a non-rotating gear. Three pinion shafts 36 each having the illustrated oil hole and supporting the planetary gear 31, and a carrier 37 that supports both ends of the pinion shaft 36 to rotatably support the planetary gear 31 and can also rotate itself. And comprising. The needle roller bearing 10 is fitted on the pinion shaft 36, the cage 11 is attached to the planetary gear 31 with an outer diameter support, and the bearing space is filled with a predetermined lubricating oil.

遊星歯車機構３０は、例えば１速の場合、太陽ギア３４をドライブ側とし、遊星歯車３１とキャリア３７とをドリブン側として、リングギア３２を固定することで、大きな減速比が得られる。また、例えば２速の場合、太陽ギア３４を固定し、遊星歯車３１とキャリア３７とをドリブン側とし、リングギア３２をドライブ側とすることで、中程度の減速比が得られる。さらに、例えば３速の場合、太陽ギア３４を固定し、遊星歯車３１とキャリア３７とをドライブ側とし、リングギア３２をドリブン側とすることで、小さな減速比が得られる。   For example, in the case of the first speed, the planetary gear mechanism 30 can obtain a large reduction ratio by fixing the ring gear 32 with the sun gear 34 as the drive side and the planetary gear 31 and the carrier 37 as the driven side. For example, in the case of the second speed, a moderate reduction ratio can be obtained by fixing the sun gear 34, the planetary gear 31 and the carrier 37 on the driven side, and the ring gear 32 on the drive side. Further, for example, in the case of the third speed, a small reduction ratio can be obtained by fixing the sun gear 34, the planetary gear 31 and the carrier 37 on the drive side, and the ring gear 32 on the driven side.

そして、これらとは異なり、例えば後退の場合、太陽ギア３４をドリブン側とし、遊星歯車３１とキャリア３７とを固定し、リングギア３２をドライブ側とすることで、入力に対して出力を逆転させることができる。このように、遊星歯車機構３０は、３速の変速と後退との減速を行うことができるが、これらの回転動作は、一例であって、必ずしもこれらの動作に限られることはない。   Unlike these, for example, in the case of reverse, the sun gear 34 is driven, the planetary gear 31 and the carrier 37 are fixed, and the ring gear 32 is driven, so that the output is reversed with respect to the input. be able to. As described above, the planetary gear mechanism 30 can perform the speed change of the third speed and the reduction of the reverse speed, but these rotational operations are merely examples, and are not necessarily limited to these operations.

このような回転動作において、ピニオンシャフト３６が有する油孔から流出してきた潤滑油は、ピニオンシャフト３６と針状ころ１２との転動面を通過し、そして遊星歯車３１の自転による遠心力で保持器１１の外径側に押し出される。その際、ピニオンシャフト３６と柱部１４とが最も接近する柱部１４の中間部において幅狭部１７により形成された隙間（流路）を介して潤滑油が保持器１１の外径側へ効率よく流動される。   In such a rotation operation, the lubricating oil flowing out from the oil hole of the pinion shaft 36 passes through the rolling surfaces of the pinion shaft 36 and the needle rollers 12 and is held by the centrifugal force due to the rotation of the planetary gear 31. It is pushed out to the outer diameter side of the vessel 11. At that time, the lubricating oil is efficiently transferred to the outer diameter side of the cage 11 through a gap (flow path) formed by the narrow portion 17 at the intermediate portion of the column portion 14 where the pinion shaft 36 and the column portion 14 are closest to each other. Well fluidized.

以上説明したように、本実施形態の針状ころ軸受１０によれば、柱部１４の中間において周方向に幅狭の幅狭部１７を通じて保持器１１の外径側および内径側からの潤滑油の流路が形成される。これにより、限られた潤滑油量で転動面での潤滑油を効率的に保持することができる。また、幅狭部１７により、柱部１４の中間において容量が減少されることで、回転時の遠心力が負荷されたとしても、柱部１４は自重に伴う変形が抑制されて、針状ころ１２に対する保持性を損なうことがない。   As described above, according to the needle roller bearing 10 of the present embodiment, the lubricating oil from the outer diameter side and the inner diameter side of the cage 11 through the narrow portion 17 that is narrow in the circumferential direction in the middle of the column portion 14. The flow path is formed. Thereby, the lubricating oil on the rolling surface can be efficiently held with a limited amount of lubricating oil. Moreover, even if the centrifugal force at the time of rotation is loaded by the capacity | capacitance reducing in the middle of the pillar part 14 by the narrow part 17, the deformation | transformation accompanying the dead weight is suppressed and the needle part 14 is suppressed. The retainability with respect to 12 is not impaired.

また、本実施形態の針状ころ軸受１０によれば、遊星歯車機構３０に組付けた場合には、ピニオンシャフト３６の油孔から流出してきた潤滑油は、ピニオンシャフト３６と針状ころ１２との転動面を通過し、そして遊星歯車３１の自転による遠心力で保持器１１の外径側に押し出される。その際、ピニオンシャフト３６と柱部１４とが最も接近する柱部１４の中間部において幅狭部１７の幅が狭くなっているために、柱部１４と針状ころ１２との間に隙間が確保され、その隙間を通じて潤滑油が保持器１１の外径側へ効率よく流動される。このため、複雑な機構で潤滑油が十分に行きわたらないとされる遊星歯車機構３０においても、限られた潤滑油量で転動面での潤滑油を効率的に保持することができる。
さらに、幅狭部１７は、撓み量が最大となる柱部１４の中間部における容量を減少させることで、遊星歯車３１の公転および自転による遠心力が負荷されたとしても、柱部１４は自重に伴う変形が抑制されることで、コーナー部への応力集中が低減されて、針状ころに対する保持性を損なうことがない。 Further, according to the needle roller bearing 10 of the present embodiment, when assembled in the planetary gear mechanism 30, the lubricating oil flowing out from the oil hole of the pinion shaft 36 is transferred to the pinion shaft 36, the needle roller 12, and the like. And is pushed to the outer diameter side of the cage 11 by the centrifugal force due to the rotation of the planetary gear 31. At that time, since the width of the narrow portion 17 is narrow at the intermediate portion of the column portion 14 where the pinion shaft 36 and the column portion 14 are closest to each other, there is a gap between the column portion 14 and the needle roller 12. As a result, the lubricating oil efficiently flows to the outer diameter side of the cage 11 through the gap. For this reason, even in the planetary gear mechanism 30 in which the lubricating oil is not sufficiently distributed by a complicated mechanism, the lubricating oil on the rolling surface can be efficiently held with a limited amount of lubricating oil.
Further, the narrow portion 17 reduces the capacity at the intermediate portion of the column portion 14 where the amount of deflection is maximized, so that the column portion 14 has its own weight even if the centrifugal force due to the revolution and rotation of the planetary gear 31 is applied. Suppressing the deformation associated with, the stress concentration on the corner portion is reduced, and the retainability to the needle rollers is not impaired.

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、変形、改良等が自在である。その他、上述した実施形態における各構成要素の材質、形状、寸法、数値、形態、数、配置場所、等は本発明を達成できるものであれば任意であり、限定されない。   In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimension, numerical value, form, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

例えば、針状ころの数、外径、長さ等については、適用される遊星歯車におけるトルク容量等を考慮して適宜設定されるために、何ら限定されるものではない。勿論、針状ころの総数、外径、長さに応じて保持器の外径、柱部の数、ポケットの数、等も要求される仕様に基づき適宜設定される。   For example, the number of needle rollers, the outer diameter, the length, and the like are not limited at all because they are appropriately set in consideration of the torque capacity and the like of the applied planetary gear. Of course, the outer diameter of the cage, the number of pillars, the number of pockets, and the like are appropriately set based on required specifications in accordance with the total number, outer diameter, and length of the needle rollers.

本発明の一実施形態に係る針状ころ軸受の外観斜視図である。1 is an external perspective view of a needle roller bearing according to an embodiment of the present invention. 図１の針状ころ軸受の一部破断側面図である。It is a partially broken side view of the needle roller bearing of FIG. 図１の針状ころ軸受を適用した遊星歯車機構の分解斜視図である。It is a disassembled perspective view of the planetary gear mechanism to which the needle roller bearing of FIG. 1 is applied. 従来の針状ころ軸受の部分断面図である。It is a fragmentary sectional view of the conventional needle roller bearing. 図４とは異なる従来の針状ころ軸受の部分断面図である。It is a fragmentary sectional view of the conventional needle roller bearing different from FIG.

符号の説明Explanation of symbols

１０ 針状ころ軸受
１１ 保持器
１２ 針状ころ
１３ 環状部
１４ 柱部
１５ ポケット
１７ 幅狭部
３０ 遊星歯車機構
３１ 遊星歯車
３６ ピニオンシャフト
３７ キャリア DESCRIPTION OF SYMBOLS 10 Needle roller bearing 11 Cage 12 Needle roller 13 Annular part 14 Column part 15 Pocket 17 Narrow part 30 Planetary gear mechanism 31 Planetary gear 36 Pinion shaft 37 Carrier

Claims (3)

軸方向に互いに間隔をあけて配置された一対の環状部と、円周方向に亙って間欠的に配置されて前記一対の環状部を連結する複数の柱部と、を有して、前記環状部と前記柱部と間に複数のポケットが形成された保持器と、前記ポケットに転動自在に保持された複数の針状ころと、を備えた針状ころ軸受であって、
前記柱部は、前記一対の環状部の周縁からそれぞれ軸方向内方に延出して軸方向両端部にそれぞれ位置する一対の端板部と、軸方向中間に位置し径方向内方に縮径されて前記一対の端板部よりも径方向内方に配設される中央板部と、前記一対の端板部の軸方向内方の端部と前記中央板部の軸方向両端部とを軸方向に対して傾斜した状態で連結する一対の斜板部と、を有し、
前記中央板部の中間に、周方向に向けて幅狭となる幅狭部が設けられ、
前記ポケットの軸方向長さをＬ１、前記中央板部の軸方向長さ寸法をＬ２、前記幅狭部の軸方向長さをＬ３とし、前記中央板部の周方向幅寸法をＬ４、前記幅狭部の周方向幅寸法をＬ５とするとき、Ｌ１＞Ｌ２＞Ｌ３、且つＬ４＞Ｌ５となるように設けられ、
これにより、前記中央板部の中間部分で、前記保持器と前記針状ころの転動面との間に潤滑油の流路となる隙間が形成されることを特徴とする針状ころ軸受。 A pair of annular portions arranged at intervals in the axial direction, and a plurality of column portions that are intermittently arranged in the circumferential direction to connect the pair of annular portions, A needle roller bearing comprising: a cage in which a plurality of pockets are formed between an annular portion and the column portion; and a plurality of needle rollers that are rotatably held in the pocket,
The column portions extend inward in the axial direction from the peripheral edges of the pair of annular portions, respectively, and a pair of end plate portions positioned at both axial ends, respectively, and are positioned in the axial direction and radially reduced in diameter. A central plate portion disposed radially inward of the pair of end plate portions, an axially inner end portion of the pair of end plate portions, and both axial end portions of the central plate portion. A pair of swash plate portions that are connected in an inclined state with respect to the axial direction,
In the middle of the central plate portion, a narrow portion that is narrow toward the circumferential direction is provided ,
The axial length of the pocket is L1, the axial length of the central plate is L2, the axial length of the narrow portion is L3, the circumferential width of the central plate is L4, and the width. When the circumferential width dimension of the narrow portion is L5, L1>L2> L3 and L4> L5 are provided.
Thus, a needle roller bearing is characterized in that a gap serving as a flow path for lubricating oil is formed between the cage and the rolling surface of the needle roller at an intermediate portion of the central plate portion . 前記幅狭部の周方向縁部は面取り加工が施されることを特徴とする請求項１に記載の針状ころ軸受。The needle roller bearing according to claim 1, wherein the circumferential edge portion of the narrow portion is chamfered. ピニオンシャフトの両端をキャリアで支持した遊星歯車機構における遊星歯車の支持に用いられる請求項１又は２に記載の針状ころ軸受。 The needle roller bearing according to claim 1 or 2 , which is used for supporting a planetary gear in a planetary gear mechanism in which both ends of a pinion shaft are supported by a carrier.
JP2007292329A 2007-11-09 2007-11-09 Needle roller bearing Active JP5012438B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007292329A JP5012438B2 (en) 2007-11-09 2007-11-09 Needle roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007292329A JP5012438B2 (en) 2007-11-09 2007-11-09 Needle roller bearing

Publications (3)

Publication Number Publication Date
JP2009115300A JP2009115300A (en) 2009-05-28
JP2009115300A5 JP2009115300A5 (en) 2010-10-21
JP5012438B2 true JP5012438B2 (en) 2012-08-29

Family

ID=40782645

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2007292329A Active JP5012438B2 (en) 2007-11-09 2007-11-09 Needle roller bearing

Country Status (1)

Country Link
JP (1) JP5012438B2 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6497833B2 (en) * 2012-10-05 2019-04-10 Ntn株式会社 Needle roller with cage
CN106246728B (en) * 2015-06-09 2021-05-18 斯凯孚公司 Radial cage for high speed bearings
JP7089369B2 (en) * 2018-01-09 2022-06-22 Ntn株式会社 Roller with cage and planetary gear support structure
JP7003783B2 (en) * 2018-03-27 2022-01-21 株式会社ジェイテクト Cage and roller

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10126217A1 (en) * 2001-05-30 2002-12-05 Ina Schaeffler Kg Rolling bearing cage
JP2005214390A (en) * 2004-02-02 2005-08-11 Nsk Ltd Needle bearing, planetary gear mechanism and pinion shaft

Also Published As

Publication number Publication date
JP2009115300A (en) 2009-05-28

Similar Documents

Publication Publication Date Title
JP6497833B2 (en) Needle roller with cage
US20070202986A1 (en) Roller bearing for planetary gear mechanism
JP2005069421A (en) Conical roller bearing
JP5012438B2 (en) Needle roller bearing
JP2013064451A (en) Eccentric rocking type speed reducer
JP2006234100A (en) Double-row angular ball bearing and pinion shaft supporting device for vehicle
JP2008303992A (en) Radial needle roller bearing
JP2017201194A (en) Speed reducer
JP2010159788A (en) Thrust roller bearing
JP2004324844A (en) Needle bearing and its retainer
JP5273442B2 (en) Radial needle roller bearings
JP2018194014A (en) Method of manufacturing cylindrical roller bearing and holder
JP2004324843A (en) Needle bearing and its retainer
JP4370907B2 (en) Ball bearing
JP2005076810A (en) Retainer for needle bearing and needle bearing
EP2042762A1 (en) Lubrication mechanism for bearing
JP2005030468A (en) Holder for needle roller bearing, and needle roller bearing
JP2017053461A (en) Planetary gear train
CN105822750B (en) Eccentric oscillating gear device
JP2005214391A (en) Needle bearing and planetary gear mechanism
JP5909893B2 (en) Radial needle bearing
JP2012163166A (en) Conical roller bearing
JP6349681B2 (en) Radial roller bearing cage and radial roller bearing
JP2017058022A (en) Supporting structure for planetary gear
JP2009204089A (en) Cage for needle roller bearing, and needle roller bearing

Legal Events

Date Code Title Description
A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20100907

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20100907

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20111208

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20111213

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20120131

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: 20120508

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20120521

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20150615

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Ref document number: 5012438

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150