JP2009204089A - Cage for needle roller bearing, and needle roller bearing - Google Patents

Cage for needle roller bearing, and needle roller bearing Download PDF

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Publication number
JP2009204089A
JP2009204089A JP2008047486A JP2008047486A JP2009204089A JP 2009204089 A JP2009204089 A JP 2009204089A JP 2008047486 A JP2008047486 A JP 2008047486A JP 2008047486 A JP2008047486 A JP 2008047486A JP 2009204089 A JP2009204089 A JP 2009204089A
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Prior art keywords
cage
needle roller
roller bearing
planetary gear
outer diameter
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Japanese (ja)
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Fumi Kikuchi
文 菊池
Hiromichi Takemura
浩道 武村
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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
    • F16C19/44—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
    • 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

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  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cage for a needle roller bearing, having reduced cost while securing reliability, and to provide the needle roller bearing. <P>SOLUTION: A difference is given to grinding work for the cage 12 to keep the surface roughness of an outer diameter guide face 12d better than the surface roughness of the end face of an annular portion 12a. This shortens a grinding work time for the end face 12e of the annular portion 12a to reduce cost. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、針状ころ軸受用の保持器及び針状ころに関し、特に信頼性を向上させることができる針状ころ軸受用の保持器及び針状ころ軸受に関する。   The present invention relates to a cage and needle rollers for needle roller bearings, and more particularly to a cage and needle roller bearings for needle roller bearings that can improve reliability.

車両等に搭載されている自動変速機において、一般的には遊星歯車機構が用いられている。ここで、針状ころ軸受は、細径のころを用いていることから、内輪外径と外輪内径との差が小さいスペースにも収めることができるので、遊星歯車機構の遊星歯車を回転自在に支持するために用いると、それを搭載した自動変速機のコンパクト化に寄与するので好ましいといえる。   In an automatic transmission mounted on a vehicle or the like, a planetary gear mechanism is generally used. Here, since the needle roller bearing uses a small diameter roller, it can be accommodated in a space where the difference between the inner ring outer diameter and the outer ring inner diameter is small, so that the planetary gear of the planetary gear mechanism can be rotated freely. It is preferable to use it for supporting because it contributes to the compactness of the automatic transmission on which it is mounted.

ところで、近年は、燃費の向上などを目的として、自動変速機においても多段化される傾向がある。しかるに、現在は４速が主流である自動変速機を、例えば５速或いは６速に多段化しようとすると、動力を伝達する遊星歯車機構の遊星歯車の自転速度及び公転速度が増大するということがある。このような仕様の変化に伴い、保持器を用いないいわゆる総ころと呼ばれる従来の針状ころ軸受に対し、より低摩擦且つ潤滑性に優れた保持器付きの針状ころ軸受が開発されている。   By the way, in recent years, there is a tendency to increase the number of stages in an automatic transmission for the purpose of improving fuel consumption. However, if the automatic transmission, which is currently in the 4th speed, is to be multistaged, for example, to the 5th or 6th speed, the rotation speed and revolution speed of the planetary gear of the planetary gear mechanism that transmits power increases. is there. Along with such changes in specifications, needle roller bearings with cages have been developed that have lower friction and better lubricity than conventional needle roller bearings called so-called full rollers that do not use cages. .

ここで、遊星歯車機構において、遊星歯車は自転しながら太陽歯車の周囲を公転しているが、このとき遊星歯車を支持する針状ころ軸受も自転すると共に、太陽歯車の周囲を公転するので、特に公転による遠心力が針状ころ軸受に付与されることとなる。従って、針状ころ軸受を保持器付きのものとした場合、保持器は、公転に基づく遠心力により外輪（遊星歯車内周面）に対して押しつけられるため、外輪と保持器との間で摺動が生じることとなる。このような摺動は、針状ころ軸受の引きずり抵抗を増大させる他、早期摩耗や異常発熱、さらには保持器の変形などを招く恐れがある。特に、保持器の外径案内面の面粗度が悪いと、いわゆるブレーキング現象により外輪に接触した保持器の回転速度が急激に低下し、保持器の柱部にころが衝突し、繰り返し応力を与えることで疲労破壊が生じる恐れがある。更に、遊星歯車の軸線方向両端側にはワッシャが配置されていることが多く、かかるワッシャと保持器とが摺接することによる摩耗などの不具合も予想される。
特開２００５−７６８１０７号公報 Here, in the planetary gear mechanism, the planetary gear revolves around the sun gear while rotating, but at this time the needle roller bearing supporting the planetary gear also rotates and revolves around the sun gear. In particular, centrifugal force due to revolution is applied to the needle roller bearing. Therefore, when the needle roller bearing is provided with a cage, the cage is pressed against the outer ring (inner peripheral surface of the planetary gear) by centrifugal force based on revolution, so that the sliding between the outer ring and the cage is performed. Movement will occur. Such sliding increases the drag resistance of the needle roller bearing, and may cause premature wear, abnormal heat generation, and deformation of the cage. In particular, if the surface roughness of the outer diameter guide surface of the cage is poor, the rotational speed of the cage that contacts the outer ring rapidly decreases due to the so-called braking phenomenon, and the roller collides with the column of the cage, causing repeated stress. There is a risk that fatigue failure will occur by applying. Further, washers are often arranged at both ends of the planetary gear in the axial direction, and problems such as wear due to sliding contact between the washers and the cage are also expected.
JP-A-2005-768107

これに対し、特許文献１においては、保持器外径および端面の摩擦や焼付きの防止として、遊星歯車の内径面と摺動する保持器外径面、ワッシャや隣接する軸受の保持器と摺動する保持器端面に研削加工および表面処理を施している。しかしながら、保持器の各部表面を研削処理すると、コストが増大するという問題がある。   On the other hand, in Patent Document 1, in order to prevent friction and seizure of the outer diameter of the cage and the end surface, the outer diameter surface of the cage that slides with the inner diameter surface of the planetary gear, the cage and the slide of the washer and the adjacent bearing. Grinding and surface treatment are applied to the moving cage end face. However, if the surface of each part of the cage is ground, there is a problem that the cost increases.

本発明は、上述した問題点に鑑みてなされたものであり、信頼性を確保しながらもコストを抑えた針状ころ軸受用の保持器及び針状ころ軸受を提供することを目的とする。   The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a retainer and a needle roller bearing for a needle roller bearing that can reduce the cost while ensuring reliability.

本発明の保持器は、遊星歯車機構において遊星歯車を回転自在に支持する針状ころ軸受用の保持器において、
前記保持器は、環状部と前記環状部から軸線方向に延在する複数の柱部とを有し、隣接する前記柱部間で、ころを保持するようになっており、更に外径案内で用いられ、前記保持器の外径案内面の粗さを、前記保持器の端面の粗さよりも良好（低く）としたことを特徴とする。 The cage of the present invention is a cage for a needle roller bearing that rotatably supports a planetary gear in a planetary gear mechanism.
The retainer has an annular portion and a plurality of column portions extending in the axial direction from the annular portion, and is configured to hold rollers between the adjacent column portions. It is used, and the roughness of the outer diameter guide surface of the cage is better (lower) than the roughness of the end surface of the cage.

遊星歯車に使用される保持器は、遊星歯車が公転した場合に受ける遠心力により保持器外径面が遊星歯車の内径面に押し付けられる。ここで、本発明者らは、アキシャル方向の荷重はラジアル荷重の１０％程度であり、保持器端面がワッシャ等に押し付けられる荷重は非常に小さいため、端面の粗さを外径面と同等にする必要はないことを見出した。これにより、例えば前記保持器の外径案内面については丁寧に研削加工を施すが、前記保持器の端面については、溶接跡の除去などに限定して粗く研削加工するなどして、前記保持器の端面の粗さを、前記保持器の外径案内面の粗さより悪い状態のままとすることで、オーバースペックとなることを防止し、研削加工時間の短縮によりコストダウンを図ることができる。   In the cage used for the planetary gear, the outer diameter surface of the cage is pressed against the inner diameter surface of the planetary gear by the centrifugal force received when the planetary gear revolves. Here, since the load in the axial direction is about 10% of the radial load, and the load on which the cage end face is pressed against a washer or the like is very small, the roughness of the end face is equal to that of the outer diameter face. I found that there is no need to do. As a result, for example, the outer diameter guide surface of the cage is carefully ground, but the end surface of the cage is roughly ground to limit the removal of welding marks, etc. By maintaining the roughness of the end face of the cage in a state worse than the roughness of the outer diameter guide surface of the cage, it is possible to prevent over-specification and to reduce costs by shortening the grinding time.

前記保持器の外径案内面の粗さの平均をＲ１とし、前記保持器の端面の粗さの平均をＲ２としたときに、以下の式を満足すると好ましい。
１．１ ≦ Ｒ２／Ｒ１ ≦ ７．０ （１） When the average roughness of the outer diameter guide surface of the cage is R1, and the average roughness of the end surface of the cage is R2, it is preferable that the following expression is satisfied.
1.1 ≦ R2 / R1 ≦ 7.0 (1)

以下、本発明の実施の形態を図面を参照して以下に詳細に説明する。図１は、本実施の形態にかかる針状ころ軸受を含む車両の自動変速機１の断面図である。図１において、エンジンのクランクシャフト２から出力されるトルクは、トルクコンバータ３を介して伝達され、更に複数列組み合わせれた遊星歯車機構４，５，６等を介して複数段に減速され、その後デファレンシャルギヤ７及びドライブシャフト８を介して、不図示の車輪に出力されるようになっている。   Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a sectional view of an automatic transmission 1 for a vehicle including a needle roller bearing according to the present embodiment. In FIG. 1, torque output from the crankshaft 2 of the engine is transmitted through a torque converter 3 and further decelerated to a plurality of stages through a plurality of planetary gear mechanisms 4, 5, 6, etc. The power is output to a wheel (not shown) via the differential gear 7 and the drive shaft 8.

図２は、遊星歯車機構４（５，６も原則的に同じ）の分解図である。図２において、遊星歯車機構４は、内歯を有するリングギヤ４ａと、外歯を有する太陽ギヤ４ｂと、リングギヤ４ａ及び太陽ギヤ４ｂに噛合する３つの遊星歯車４ｃと、３つのピニオンシャフト４ｅにより遊星歯車４ｃを回転自在に支持すると共に、自らも回転可能なキャリヤ４ｄとを有する。   FIG. 2 is an exploded view of the planetary gear mechanism 4 (5 and 6 are basically the same). In FIG. 2, the planetary gear mechanism 4 includes a ring gear 4a having internal teeth, a sun gear 4b having external teeth, three planetary gears 4c meshing with the ring gear 4a and the sun gear 4b, and three pinion shafts 4e. The gear 4c is rotatably supported, and has a carrier 4d that can also rotate.

遊星歯車機構４の作動原理を図３に示す。まず、１速の場合、図３（ａ）に示すように、太陽歯車４ｂをドライブ側とし、遊星歯車４ｃ（キャリヤ）をドリブン側とし、リングギヤ４ａを固定することで、大きな減速比が得られる。次に、２速の場合、図３（ｂ）に示すように、太陽歯車４ｂを固定し、遊星歯車４ｃ（キャリヤ）をドリブン側とし、リングギヤ４ａをドライブ側とすることで、中程度の減速比が得られる。更に、３速の場合、図３（ｃ）に示すように、太陽歯車４ｂを固定し、遊星歯車４ｃ（キャリヤ）をドライブ側とし、リングギヤ４ａをドリブン側とすることで、小さな減速比が得られる。尚、後退の場合、図３（ｄ）に示すように、太陽歯車４ｂをドリブン側とし、遊星歯車４ｃ（キャリヤ）を固定し、リングギヤ４ａ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。なお、以上は遊星歯車機構４の動作の一例を示すものであり、必ずしもかかる動作に限られることはない。   The operating principle of the planetary gear mechanism 4 is shown in FIG. First, in the case of the first speed, as shown in FIG. 3A, a large reduction ratio can be obtained by setting the sun gear 4b to the drive side, the planetary gear 4c (carrier) to the driven side, and fixing the ring gear 4a. . Next, in the case of the second speed, as shown in FIG. 3 (b), the sun gear 4b is fixed, the planetary gear 4c (carrier) is set to the driven side, and the ring gear 4a is set to the drive side. A ratio is obtained. Further, in the case of the third speed, as shown in FIG. 3 (c), the sun gear 4b is fixed, the planetary gear 4c (carrier) is set to the drive side, and the ring gear 4a is set to the driven side, thereby obtaining a small reduction ratio. It is done. In the case of reverse, as shown in FIG. 3 (d), the sun gear 4b is driven, the planetary gear 4c (carrier) is fixed, and the ring gear 4a is driven, so that output is output with respect to the input. Can be reversed. In addition, the above shows an example of the operation of the planetary gear mechanism 4, and the operation is not necessarily limited to this operation.

図４は、本実施の形態の針状ころ軸受を遊星歯車機構に組み込んだ状態で示す図である。図４に示すように、針状ころ軸受１０は、ピニオンシャフト（内輪）４ｅと遊星歯車（外輪）４ｃとの間に配置され、遊星歯車４ｃを回転自在に支持している。針状ころ軸受１０は、複数のころ１１と、それらを保持する保持器１２とからなっている。ピニオンシャフト４ｅ内には、図４で右方から軸線に沿って延在し、かつ中央で外周面に抜ける油路４ｆが形成されている。保持器１２は外輪案内で用いられる。尚、キャリヤ４ｄと遊星歯車４ｃとの間には、ワッシャ４ｇが配置されている。   FIG. 4 is a view showing the needle roller bearing of the present embodiment incorporated in a planetary gear mechanism. As shown in FIG. 4, the needle roller bearing 10 is disposed between a pinion shaft (inner ring) 4e and a planetary gear (outer ring) 4c, and rotatably supports the planetary gear 4c. The needle roller bearing 10 includes a plurality of rollers 11 and a cage 12 that holds them. In the pinion shaft 4e, there is formed an oil passage 4f extending along the axis from the right side in FIG. 4 and passing through the outer peripheral surface at the center. The cage 12 is used for outer ring guidance. A washer 4g is disposed between the carrier 4d and the planetary gear 4c.

図５は、本実施の形態にかかる針状ころ軸受の保持器の斜視図である。図に示すように、保持器１２は、一対の環状部１２ａを複数の柱部１２ｂで連結した構成を有している。隣接する柱部１２ｂの間が、ころ１１を保持するポケットとなる。各柱部１２ｂは、軸線方向中央において縮径した（即ち保持器１２の軸線に近接した）縮径部１２ｃを有しており、縮径部１２ｃの軸線方向両側から環状部１２ａにかけて拡径している外周面（図においてダブルハッチングで示す）を、外径案内面（すなわち外輪と摺接する面）１２ｄとしている。このような形状を有する保持器１２をＭ型保持器と呼ぶ。   FIG. 5 is a perspective view of the cage of the needle roller bearing according to the present embodiment. As shown in the figure, the cage 12 has a configuration in which a pair of annular portions 12a are connected by a plurality of column portions 12b. A space for holding the rollers 11 is formed between the adjacent column portions 12b. Each column portion 12b has a reduced diameter portion 12c that is reduced in diameter in the center in the axial direction (that is, close to the axial line of the cage 12), and expands from both sides in the axial direction of the reduced diameter portion 12c to the annular portion 12a. The outer peripheral surface (indicated by double hatching in the figure) is an outer diameter guide surface (that is, a surface in sliding contact with the outer ring) 12d. The cage 12 having such a shape is called an M-type cage.

本実施の形態においては、１枚の板材をパンチして柱部を形成し、その後丸めて両端を溶接することで、保持器１２を形成している。従って、そのままでは外径案内面１２ｄの面粗度が悪いため、研削加工を施すことで、外径案内面１２ｄが遊星歯車４ｃの内周面と摺接したような場合でも、摩擦を低く抑えることができる。それにより、針状ころ軸受１０の引きずり抵抗を減少させ、早期摩耗や異常発熱を抑制し、さらには保持器１２の変形や破損を招くブレーキング現象の発生を抑制することができる。又、保持器１２の環状部１２ａの端面１２ｅも、溶接の影響で面粗度が悪くなる傾向があるが、研削加工で溶接跡を除去し、その面粗度を向上させ、環状部１２ａがワッシャと摺接したときにおける摩擦を低く抑えることができる。   In the present embodiment, the retainer 12 is formed by punching one plate material to form a column portion, and then rounding and welding both ends. Accordingly, since the surface roughness of the outer diameter guide surface 12d is poor as it is, the grinding is performed to keep the friction low even when the outer diameter guide surface 12d is in sliding contact with the inner peripheral surface of the planetary gear 4c. be able to. Thereby, the drag resistance of the needle roller bearing 10 can be reduced, early wear and abnormal heat generation can be suppressed, and further, the occurrence of a braking phenomenon that causes deformation or breakage of the cage 12 can be suppressed. Further, the end surface 12e of the annular portion 12a of the cage 12 also tends to have poor surface roughness due to the effect of welding. However, the welding surface is removed by grinding to improve the surface roughness. Friction at the time of sliding contact with the washer can be kept low.

但し、本実施の形態では、上記の研削加工に差を付けて、外径案内面１２ｄの面粗度を環状部１２ａ端面の面粗度よりも良好としている。これにより、環状部１２ａの端面１２ｅの研削加工時間を短縮することができ、コストダウンが可能となる。かかる技術は、保持器の環状部が柱部に対して半径方向に突出していない、いわゆる波型保持器についても同様に適用が可能である。なお、リン酸マンガン等の被膜を施しても同様の効果が得られるが、外径案内面１２ｄの面粗度を環状部１２ａ端面の面粗度よりも良好とするのが望ましい。   However, in this embodiment, the surface roughness of the outer diameter guide surface 12d is made better than the surface roughness of the end surface of the annular portion 12a by making a difference in the grinding process. Thereby, the grinding time of the end surface 12e of the annular portion 12a can be shortened, and the cost can be reduced. Such a technique can be similarly applied to a so-called corrugated cage in which the annular portion of the cage does not protrude in the radial direction with respect to the column portion. Although the same effect can be obtained by applying a coating such as manganese phosphate, it is desirable that the surface roughness of the outer diameter guide surface 12d be better than the surface roughness of the end surface of the annular portion 12a.

本発明者らは、本発明の効果を確認する試験を行った。かかる試験は、保持器の公転試験機を用いて、以下の条件で行った。試験結果を表１に示す。
キャリア公転数：７５００ｍｉｎ-1
ピニオン自転数：１００００ｍｉｎ-1
キャリア公転半径：４０ｍｍ
ギヤ内径と保持器のＰＶ値：３００ＭＰａ・ｍ／ｓ
潤滑油：ＡＴＦ
潤滑油供給量：０．１Ｌ／ｍｉｎ The present inventors conducted a test to confirm the effect of the present invention. Such a test was conducted using the cage revolution tester under the following conditions. The test results are shown in Table 1.
Number of career revolutions: 7500 min -1
Pinion rotation speed: 10000 min -1
Carrier revolution radius: 40mm
Gear inner diameter and cage PV value: 300 MPa · m / s
Lubricating oil: ATF
Lubricating oil supply amount: 0.1 L / min

Figure 2009204089
Figure 2009204089

表１の試験結果によれば、保持器の外径案内面の粗さ（Ｒａ）の平均をＲ１とし、保持器の端面の粗さ（Ｒａ）の平均をＲ２としたときに、Ｒ２／Ｒ１が１．１以上、７．０以下の範囲で、カジリや摩耗が発生しなかったのに対し、Ｒ２／Ｒ１が１．０のときに、ギヤ・ワッシャにカジリが発生し、Ｒ２／Ｒ１が０．５のときに、ギヤ内径に摩耗が発生し、Ｒ２／Ｒ１が７．５のときに、ワッシャ摩耗が発生した。以上より、Ｒ２／Ｒ１は以下の範囲であることが望ましい。
１．１ ≦ Ｒ２／Ｒ１ ≦ ７．０ （１） According to the test results in Table 1, when the average roughness (Ra) of the outer diameter guide surface of the cage is R1, and the average roughness (Ra) of the end surface of the cage is R2, R2 / R1 In the range from 1.1 to 7.0, no galling or wear occurred, but when R2 / R1 was 1.0, galling occurred in the gear washer, and R2 / R1 was When 0.5, wear occurred in the gear inner diameter, and when R2 / R1 was 7.5, washer wear occurred. Accordingly, R2 / R1 is preferably in the following range.
1.1 ≦ R2 / R1 ≦ 7.0 (1)

以上、本発明を実施例を参照して説明してきたが、本発明は上記実施の形態に限定して解釈されるべきではなく、適宜変更・改良が可能であることはもちろんである。例えば、保持器の焼付き防止として、肌焼鋼（例えばＳＣＭ４１５）に浸炭窒化することにより、耐摩耗性を向上させることができる。   The present invention has been described with reference to the embodiments. However, the present invention should not be construed as being limited to the above-described embodiments, and can be modified or improved as appropriate. For example, the wear resistance can be improved by carbonitriding to a case-hardened steel (for example, SCM415) as prevention of seizure of the cage.

本実施の形態にかかる針状ころ軸受を含む車両の自動変速機の断面図である。It is sectional drawing of the automatic transmission of the vehicle containing the needle roller bearing concerning this Embodiment. 遊星歯車機構４の分解図である。4 is an exploded view of the planetary gear mechanism 4. FIG. 遊星歯車機構の作動原理を示す図である。It is a figure which shows the operating principle of a planetary gear mechanism. 本実施の形態の針状ころ軸受を遊星歯車機構に組み込んだ状態で示す図である。It is a figure shown in the state where the needle roller bearing of this embodiment was built in the planetary gear mechanism. 本実施の形態の針状ころ軸受における保持器の斜視図である。It is a perspective view of the holder | retainer in the needle roller bearing of this Embodiment.

符号の説明Explanation of symbols

１ 自動変速機
４〜６ 遊星歯車機構
１０ 針状ころ軸受
１１ ころ
１２ 保持器 DESCRIPTION OF SYMBOLS 1 Automatic transmission 4-6 Planetary gear mechanism 10 Needle roller bearing 11 Roller 12 Cage

Claims (3)

遊星歯車機構において遊星歯車を回転自在に支持する針状ころ軸受用の保持器において、
前記保持器は、環状部と前記環状部から軸線方向に延在する複数の柱部とを有し、隣接する前記柱部間で、ころを保持するようになっており、更に外径案内で用いられ、前記保持器の外径案内面の粗さを、前記保持器の端面の粗さよりも良好としたことを特徴とする針状ころ軸受用の保持器。 In a cage for a needle roller bearing that rotatably supports a planetary gear in a planetary gear mechanism,
The retainer has an annular portion and a plurality of column portions extending in the axial direction from the annular portion, and is configured to hold rollers between the adjacent column portions. A retainer for a needle roller bearing, wherein the outer diameter guide surface of the retainer has a roughness greater than that of an end surface of the retainer. 前記保持器の外径案内面の粗さの平均をＲ１とし、前記保持器の端面の粗さの平均をＲ２としたときに、以下の式を満足することを特徴とする請求項１に記載の針状ころ軸受用の保持器。
１．１ ≦ Ｒ２／Ｒ１ ≦ ７．０ （１） The following formula is satisfied, where R1 is an average roughness of the outer diameter guide surface of the cage, and R2 is an average roughness of the end surface of the cage. Cage for needle roller bearings.
1.1 ≦ R2 / R1 ≦ 7.0 (1) 請求項１又は２に記載の針状ころ軸受用の保持器を用いたことを特徴とする針状ころ軸受。   A needle roller bearing using the cage for a needle roller bearing according to claim 1 or 2.
JP2008047486A 2008-02-28 2008-02-28 Cage for needle roller bearing, and needle roller bearing Pending JP2009204089A (en)

Priority Applications (1)

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Publication Number Publication Date
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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021140836A1 (en) * 2020-01-09 2021-07-15 Ntn株式会社 Welded retainer for roller bearing, roller with retainer, and roller bearing

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021140836A1 (en) * 2020-01-09 2021-07-15 Ntn株式会社 Welded retainer for roller bearing, roller with retainer, and roller bearing

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