[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

JP3196443B2 - Roller bearing - Google Patents

Roller bearing

Info

Publication number
JP3196443B2
JP3196443B2 JP21104593A JP21104593A JP3196443B2 JP 3196443 B2 JP3196443 B2 JP 3196443B2 JP 21104593 A JP21104593 A JP 21104593A JP 21104593 A JP21104593 A JP 21104593A JP 3196443 B2 JP3196443 B2 JP 3196443B2
Authority
JP
Japan
Prior art keywords
roller
roller bearing
raceway
rolling
circumferential direction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP21104593A
Other languages
Japanese (ja)
Other versions
JPH0742743A (en
Inventor
敏晴 本田
弘志 岩佐
茂一 千葉
保夫 村上
敏之 山本
保行 島崎
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 JP21104593A priority Critical patent/JP3196443B2/en
Priority to US08/284,977 priority patent/US5456538A/en
Publication of JPH0742743A publication Critical patent/JPH0742743A/en
Application granted granted Critical
Publication of JP3196443B2 publication Critical patent/JP3196443B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Landscapes

  • Rolling Contact Bearings (AREA)

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【0001】[0001]

【産業上の利用分野】この発明に係るころ軸受は、例え
ば自動車用自動変速機に使用する、総ころ型の針状ころ
軸受として利用出来る。
BACKGROUND OF THE INVENTION The roller bearing according to the present invention can be used as a full-roller needle roller bearing for use in, for example, an automatic transmission for an automobile.

【0002】[0002]

【従来の技術】例えば自動車用自動変速機の遊星歯車機
構の回転支持部分には、総ころ型の針状ころ軸受(所謂
ニードル軸受)等のころ軸受が組み込まれている。この
様なころ軸受の寿命を確保する為には、複数本のころの
転動面と、外輪軌道、内輪軌道等、この転動面が線接触
する相手部材の周面に形成した軌道面とが線接触する、
転動部分の潤滑状態が良好である必要がある。特に、自
動変速機用遊星歯車機構の場合、ころ軸受装着部分への
潤滑油の供給量が必ずしも十分に確保されないので、上
記転動部分の潤滑状態を良好にする考慮が必要になる。
2. Description of the Related Art For example, a roller bearing such as a full roller type needle roller bearing (a so-called needle bearing) is incorporated in a rotation supporting portion of a planetary gear mechanism of an automatic transmission for an automobile. In order to ensure the service life of such a roller bearing, the rolling surfaces of a plurality of rollers and the raceway surfaces formed on the peripheral surface of a mating member such as an outer raceway, an inner raceway or the like, where the rolling surfaces are in line contact with each other, are required. Are in line contact,
The lubrication state of the rolling parts needs to be good. In particular, in the case of a planetary gear mechanism for an automatic transmission, a sufficient amount of lubricating oil is not necessarily ensured to the roller bearing mounting portion, and therefore, consideration must be given to improving the lubrication state of the rolling portion.

【0003】この為従来は、上記転動面並びに軌道面を
極力平滑に仕上げ、少ない潤滑油でもこれら転動面と軌
道面との間で、上記ころと相手部材とが金属接触する事
を防止する様にしていた。
Conventionally, the rolling surface and the raceway surface have been finished as smooth as possible to prevent metal contact between the roller and the mating member between the rolling surface and the raceway surface even with a small amount of lubricating oil. I was doing it.

【0004】[0004]

【発明が解決しようとする課題】ところが、単に転動面
並びに軌道面を平滑に仕上げただけでは、著しい場合に
はころ軸受が焼き付く可能性が指摘されている。即ち、
ころ軸受の運転時に複数本のころには、各ころの中心軸
と相手部材の中心軸とを非平行にする(スキューさせ
る)方向のモーメントが加わる場合がある。この様なモ
ーメントが加わった場合に、上記転動面並びに軌道面が
単に平滑であると、上記各ころが殆どこのモーメントに
対抗する事なく、スキューしてしまう。
However, it has been pointed out that if the rolling surface and the raceway surface are simply finished to be smooth, the roller bearing may seize in a remarkable case. That is,
During operation of the roller bearing, a moment in a direction in which the central axis of each roller and the central axis of the mating member are made non-parallel (skew) may be applied to the plurality of rollers. When such a moment is applied, if the rolling surface and the raceway surface are simply smooth, each roller skews almost without opposing this moment.

【0005】ころがスキューした場合には、各ころが回
転する事に対する抵抗が、スキューする以前に比べて極
端に大きくなり、ころ軸受部分での発熱量が著しく増大
する。そして、著しい場合には、上記ころ軸受部分が焼
き付く恐れがある。
[0005] When the rollers are skewed, the resistance to rotation of each roller is extremely large as compared to before the skew, and the amount of heat generated at the roller bearings is significantly increased. In a remarkable case, there is a possibility that the roller bearing portion is seized.

【0006】この様な不都合を生じるスキューを防止す
る為に、例えば特公昭57−61933号公報には、外
輪軌道の粗さを内輪軌道の粗さよりも大きく(粗く)
し、各ころの転動面と外輪軌道との摩擦係数を、各ころ
の転動面と内輪軌道との摩擦係数よりも大きくする技術
が記載されている。しかしながら、この様な従来技術で
は、ころのスキューを防止する効果が必ずしも十分では
なく、上記モーメントが大きい場合には、ころのスキュ
ーを十分に防止出来ない。本発明のころ軸受は、この様
な事情に鑑みて発明されたものである。
In order to prevent the skew which causes such inconvenience, for example, Japanese Patent Publication No. 57-61933 discloses that the roughness of an outer raceway is larger (rougher) than that of an inner raceway.
In addition, a technique is described in which the friction coefficient between the rolling surface of each roller and the outer raceway is larger than the friction coefficient between the rolling surface of each roller and the inner raceway. However, in such a conventional technique, the effect of preventing roller skew is not always sufficient, and when the moment is large, the roller skew cannot be sufficiently prevented. The roller bearing of the present invention has been invented in view of such circumstances.

【0007】[0007]

【課題を解決するための手段】本発明のころ軸受は、従
来のころ軸受と同様に、外周面を転動面とした複数のこ
ろと、周面をこの転動面と線接触する軌道面とした相手
部材とを備えている。特に、本発明のころ軸受に於いて
は、上記転動面の軸方向並びに円周方向に亙る表面粗さ
が、何れも0.06μmRa以下であり、上記相手部材の
周面の表面粗さは、軸方向に亙っては0.08〜0.1
5μmRaであり、円周方向に亙っては0.04μmRa以
下である事を特徴としている。
A roller bearing according to the present invention comprises a plurality of rollers having an outer peripheral surface as a rolling surface and a raceway surface having a peripheral surface in line contact with the rolling surface, similarly to a conventional roller bearing. And a mating member. In particular, in the roller bearing of the present invention, the surface roughness of the rolling surface in both the axial direction and the circumferential direction is 0.06 μmRa or less, and the surface roughness of the peripheral surface of the mating member is less than 0.06 μmRa. 0.08 to 0.1 in the axial direction
5 μm Ra, and is not more than 0.04 μm Ra in the circumferential direction.

【0008】[0008]

【作用】上述の様に構成される本発明のころ軸受の場
合、ころをスキューさせる方向のモーメントが作用した
場合でも、ころの転動面と相手部材の軌道面との間に、
ころのスキューを阻止する方向の摩擦力が作用して、こ
ろがスキューする事がなくなる。
In the case of the roller bearing of the present invention configured as described above, even when a moment acting in the direction of skewing the roller acts, the roller bearing is positioned between the rolling surface of the roller and the raceway surface of the mating member.
The frictional force acting in the direction to prevent the skew of the roller acts, so that the roller does not skew.

【0009】この状態を、図1〜3により説明する。こ
の図1〜3は、ころ1の転動面2と内輪3の外周面に設
けた、軌道面である内輪軌道4との接触状態を工夫する
事で、上記ころ1がスキューするのを防止するものであ
る。本発明のころ軸受の場合、図1〜3から明らかな様
に、上記内輪軌道4の表面粗さを、軸方向(図1〜2の
左右方向、図3の左右方向)に亙っては比較的粗く
(0.08〜0.15μmRa)、円周方向に亙っては比
較的滑らかに(0.04μmRa以下)している。即ち、
軸方向に亙る表面粗さと円周方向に亙る表面粗さとの比
(軸方向に亙る表面粗さ/円周方向に亙る表面粗さ)を
2以上にしている。
This state will be described with reference to FIGS. FIGS. 1 to 3 show that the roller 1 is prevented from skew by devising a state of contact between a rolling surface 2 of the roller 1 and an inner raceway 4 which is a raceway surface provided on an outer peripheral surface of the inner race 3. Is what you do. In the case of the roller bearing of the present invention, as is apparent from FIGS. 1 to 3, the surface roughness of the inner raceway 4 is not changed in the axial direction (the left-right direction in FIGS. 1 and 2 and the left-right direction in FIG. 3). It is relatively rough (0.08 to 0.15 μm Ra) and relatively smooth (0.04 μm Ra or less) in the circumferential direction. That is,
The ratio of the surface roughness in the axial direction to the surface roughness in the circumferential direction (surface roughness in the axial direction / surface roughness in the circumferential direction) is 2 or more.

【0010】この様に、軸方向に亙る表面粗さと円周方
向に亙る表面粗さとの間に差を設けた内輪軌道4にころ
1の転動面2を当接させつつころ1を転動させた状態
で、このころ1に、このころ1をスキューさせる方向の
モーメントMが作用した場合、ころ1には、このモーメ
ントMに対抗して、ころ1がスキューするのを阻止する
方向の力が作用する。
As described above, the roller 1 is rolled while the rolling surface 2 of the roller 1 is brought into contact with the inner raceway 4 having a difference between the surface roughness in the axial direction and the surface roughness in the circumferential direction. In this state, when a moment M in the direction of skewing the roller 1 acts on the roller 1, a force in the direction of preventing the roller 1 from skewing against the moment M is applied to the roller 1. Works.

【0011】即ち、ころ1がスキューする傾向になる
と、上記転動面2と内輪軌道4との間の摩擦状態が、転
がり摩擦だけでなく滑り摩擦が混在する状態となる。こ
の滑り摩擦によって、上記両面2、4(転動面2と内輪
軌道4とを指す。以下、同様。)の軸方向並びに円周方
向に亙って摩擦し合う傾向となるが、本発明のころ軸受
の場合には、上記内輪軌道4の軸方向に亙る表面粗さ
が、円周方向に亙る表面粗さよりも大きい為、上記両面
2、4の軸方向に亙る摩擦力が、円周方向に亙る摩擦力
よりも大きくなる。そして、比較的大きな軸方向に亙る
滑り摩擦力によって上記ころ1に、上記モーメントMに
対抗してころ1のスキューを防止する方向の力が発生す
る。
That is, when the rollers 1 tend to skew, the friction state between the rolling surface 2 and the inner raceway 4 becomes a state in which not only rolling friction but also sliding friction is mixed. The sliding friction tends to cause friction in both the axial direction and the circumferential direction of the two surfaces 2 and 4 (the rolling surface 2 and the inner raceway 4; the same applies hereinafter). In the case of a roller bearing, the surface roughness of the inner raceway 4 in the axial direction is larger than the surface roughness of the inner raceway 4 in the circumferential direction. Is greater than the frictional force over Then, a relatively large sliding friction force in the axial direction generates a force against the moment 1 in the roller 1 to prevent the roller 1 from being skewed.

【0012】尚、この様に、ころ1のスキューを防止す
る効果は、内輪軌道4に代えて(或は内輪軌道4と共
に)外輪の内周面に形成した外輪軌道の表面粗さを、軸
方向(図1〜2の左右方向、図3の左右方向)に亙って
は比較的粗く(0.08〜0.15μmRa)、円周方向
に亙っては比較的滑らかに(0.04μmRa以下)した
場合でも、同様に得られる。
As described above, the effect of preventing the skew of the rollers 1 is that the surface roughness of the outer raceway formed on the inner peripheral surface of the outer race instead of (or together with the inner raceway 4) In the direction (the left-right direction in FIGS. 1 and 2 and the left-right direction in FIG. 3), it is relatively coarse (0.08 to 0.15 μmRa), and relatively smooth in the circumferential direction (0.04 μmRa). Below), the same can be obtained.

【0013】これに対して、図4〜6に示す様に、内輪
軌道4(或は外輪軌道)の表面粗さを、軸方向と円周方
向とでほぼ等しくした場合には、内輪軌道4の表面粗さ
の程度に関係なく、ころ1のスキューを防止する方向の
力が十分には発生しない。即ち、上記表面粗さが軸方向
と円周方向との何れの方向でも小さい(滑らかな)場合
には、上記スキューに対抗する為の力を発生させる程の
摩擦力が、前記両面2、4間に作用せず、ころ1のスキ
ュー防止を図れない。又、上記表面粗さが軸方向と円周
方向との何れの方向でも大きい(粗い)場合には、軸方
向に亙る滑り摩擦力だけでなく、円周方向に亙る滑り摩
擦力も大きくなる為、円周方向に亙る摩擦力によって、
スキューしたころを元に戻す力が消され、ころ1のスキ
ュー防止効果がなくなる。更に、表面粗さを両方向に亙
って大きくすると、前記両面2、4間の潤滑性が悪化
し、転がり疲労に対する悪影響が発生して、ころ軸受の
寿命が短くなる。
On the other hand, as shown in FIGS. 4 to 6, when the surface roughness of the inner raceway 4 (or the outer raceway) is substantially equal in the axial direction and the circumferential direction, the inner raceway 4 Irrespective of the degree of surface roughness of the roller 1, a force in the direction to prevent the skew of the roller 1 is not sufficiently generated. That is, when the surface roughness is small (smooth) in both the axial direction and the circumferential direction, the frictional force enough to generate a force for countering the skew is generated on the two surfaces 2 and 4. No skew of the roller 1 can be prevented without acting in the middle. When the surface roughness is large (rough) in both the axial direction and the circumferential direction, not only the sliding friction force in the axial direction but also the sliding friction force in the circumferential direction is increased. By frictional force in the circumferential direction,
The force to return the skewed roller to its original state is erased, and the effect of preventing the roller 1 from skew is lost. Further, when the surface roughness is increased in both directions, the lubricity between the two surfaces 2 and 4 is deteriorated, adversely affecting rolling fatigue occurs, and the life of the roller bearing is shortened.

【0014】[0014]

【実施例】本発明の効果を確認する為、本発明者が行な
った実験の結果に就いて、図7〜9並びに第1表の記載
を参照しつつ説明する。
EXAMPLES In order to confirm the effects of the present invention, the results of experiments conducted by the present inventors will be described with reference to FIGS. 7 to 9 and Table 1.

【0015】図7は、実験に使用した装置を示してい
る。互いに同心に、且つ間隔をあけて配置された1対の
ホルダ5a、5bの間には中空の固定軸6を、両ホルダ
5a、5bに掛け渡す様に支持している。この固定軸6
内には一方のホルダ5bから潤滑油が送り込まれ、この
潤滑油は吐出孔7を通じて、上記固定軸6の周囲に吐出
される。この様な固定軸6の外周面を、軌道面である内
輪軌道4としている。
FIG. 7 shows the apparatus used for the experiment. A hollow fixed shaft 6 is supported between a pair of holders 5a and 5b arranged concentrically and spaced apart from each other so as to span both holders 5a and 5b. This fixed shaft 6
The lubricating oil is fed into the inside from one of the holders 5 b, and the lubricating oil is discharged around the fixed shaft 6 through the discharge holes 7. The outer peripheral surface of the fixed shaft 6 is the inner raceway 4 which is the raceway surface.

【0016】一方、上記固定軸6の周囲には外輪8を、
この固定軸6と同心に、且つ回転自在に支持している。
即ち、外輪8の内周面に形成した外輪軌道9と上記内輪
軌道4との間に複数のころ1、1を転動自在に設けて、
上記固定軸6の周囲に外輪8を、回転自在に支持してい
る。ころ1、1を保持する為の保持器は設けない。
On the other hand, an outer ring 8 is provided around the fixed shaft 6,
The fixed shaft 6 is supported concentrically and rotatably.
That is, a plurality of rollers 1 and 1 are provided between the outer raceway 9 formed on the inner peripheral surface of the outer race 8 and the inner raceway 4 so as to roll freely.
An outer ring 8 is rotatably supported around the fixed shaft 6. No retainer for retaining rollers 1 and 1 is provided.

【0017】上記外輪8の端部(図7の右端部)外周面
には従動歯車10を外嵌固定し、この従動歯車10と、
モータ11により回転駆動される駆動歯車12とを噛合
させる事で、上記外輪8を16000r.p.m.で回転させ
る。又、この外輪8の周囲には、背面合わせで組み合わ
された1対のアンギュラ型の玉軸受13、13を介し
て、抑え輪14を設けている。そして、この抑え輪14
に、2500Nのラジアル加重と、14N・mのモーメ
ント加重とを加える。
A driven gear 10 is externally fitted and fixed to an outer peripheral surface of an end (right end in FIG. 7) of the outer ring 8.
The outer ring 8 is rotated at 16000 rpm by meshing with a drive gear 12 that is rotationally driven by a motor 11. In addition, a retaining ring 14 is provided around the outer ring 8 via a pair of angular type ball bearings 13, 13 which are combined back to back. And this retaining ring 14
, A radial load of 2500 N and a moment load of 14 N · m.

【0018】この様な試験装置を使用して、前記固定軸
6外周面の内輪軌道4並びにころ1、1の転動面2、2
の表面粗さを変えつつ、上記内輪軌道4の温度を測定し
たところ、次の第1表に示す様な結果を得られた。尚、
第1表中で表面粗さの値は、JIS B 0601に規定された中
心線平均粗さで、単位はμmRa である。内輪軌道4の温
度の単位は℃である。
Using such a test apparatus, the inner raceway 4 on the outer peripheral surface of the fixed shaft 6 and the rolling surfaces 2, 2 of the rollers 1, 1 are used.
When the temperature of the inner ring raceway 4 was measured while changing the surface roughness of the above, the results shown in the following Table 1 were obtained. still,
In Table 1, the value of the surface roughness is the center line average roughness specified in JIS B 0601, and the unit is μmRa. The unit of the temperature of the inner raceway 4 is ° C.

【0019】第1表Table 1

【表1】 [Table 1]

【0020】この第1表の記載から明らかな通り、本発
明のころ軸受は従来のころ軸受に比べて、内輪軌道4部
分の温度上昇を低く抑える事が出来る。又、本発明のこ
ろ軸受の場合、内輪軌道4部分の温度変化も、図8に示
す様に極く少ないものであった。これに対して、従来の
ころ軸受の場合には、図9に示す様に、内輪軌道4部分
の温度が大きく変化した。
As is clear from the description in Table 1, the roller bearing of the present invention can suppress the temperature rise of the inner ring raceway 4 portion lower than the conventional roller bearing. Further, in the case of the roller bearing of the present invention, the temperature change in the inner ring raceway 4 was very small as shown in FIG. On the other hand, in the case of the conventional roller bearing, as shown in FIG. 9, the temperature of the inner ring raceway 4 greatly changed.

【0021】尚、構成各部材の表面を所望の性状に加工
するのは、砥石の砥粒や結合剤として適宜のものを使用
し、センタレス加工等、加工法を工夫する事で行なえ
る。例えば、熔融アルミナ質の砥粒と樹脂質結合剤とで
形成される砥石を用い、被加工物の送り速度等を適当に
設定して研削加工を行なう事で、所望の表面性状を有す
る部材を得られる。
The surfaces of the constituent members can be machined into desired properties by using appropriate abrasive grains and binders of the grindstone and devising a machining method such as centerless machining. For example, using a grindstone formed of fused alumina abrasive grains and a resinous binder, by appropriately setting the feed speed and the like of the workpiece and performing a grinding process, a member having a desired surface property can be obtained. can get.

【0022】[0022]

【発明の効果】本発明のころ軸受は、以上に述べた様に
構成され作用するので、ころ軸受部分での発熱量を少な
く抑えて、上記ころ軸受部分が焼き付く危険性を少なく
出来る。
Since the roller bearing of the present invention is constructed and operates as described above, the amount of heat generated at the roller bearing portion can be reduced, and the risk of seizure of the roller bearing portion can be reduced.

【図面の簡単な説明】[Brief description of the drawings]

【図1】本発明のころ軸受を模式的に示す斜視図。FIG. 1 is a perspective view schematically showing a roller bearing of the present invention.

【図2】同じく円周方向から見た図。FIG. 2 is a view similarly viewed from a circumferential direction.

【図3】同じく軸方向から見た図。FIG. 3 is a diagram viewed from the same axial direction.

【図4】従来のころ軸受を模式的に示す斜視図。FIG. 4 is a perspective view schematically showing a conventional roller bearing.

【図5】同じく円周方向から見た図。FIG. 5 is a view similarly viewed from a circumferential direction.

【図6】同じく軸方向から見た図。FIG. 6 is a diagram viewed from the axial direction.

【図7】本発明の効果を確認する為に行なった試験装置
の断面図。
FIG. 7 is a cross-sectional view of a test device performed to confirm the effects of the present invention.

【図8】本発明のころ軸受の軌道面の温度変化を示す線
図。
FIG. 8 is a diagram showing a temperature change of a raceway surface of the roller bearing of the present invention.

【図9】従来のころ軸受の軌道面の温度変化を示す線
図。
FIG. 9 is a diagram showing a temperature change of a raceway surface of a conventional roller bearing.

【符号の説明】[Explanation of symbols]

1 ころ 2 転動面 3 内輪 4 内輪軌道 5a、5b ホルダ 6 固定軸 7 吐出孔 8 外輪 9 外輪軌道 10 従動歯車 11 モータ 12 駆動歯車 13 玉軸受 14 抑え輪 DESCRIPTION OF SYMBOLS 1 Roller 2 Rolling surface 3 Inner ring 4 Inner ring track 5a, 5b Holder 6 Fixed shaft 7 Discharge hole 8 Outer ring 9 Outer ring track 10 Follower gear 11 Motor 12 Drive gear 13 Ball bearing 14 Retaining ring

───────────────────────────────────────────────────── フロントページの続き (72)発明者 山本 敏之 群馬県高崎市請地町11−1 (72)発明者 島崎 保行 群馬県安中市中宿646−1 (56)参考文献 特開 平4−39412(JP,A) 特開 平3−292416(JP,A) 特開 平3−117725(JP,A) (58)調査した分野(Int.Cl.7,DB名) F16C 19/00 - 19/56 F16C 33/30 - 33/66 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Toshiyuki Yamamoto 11-1 Okuchicho, Takasaki City, Gunma Prefecture (72) Inventor Yasuyuki Shimazaki 646-1 Nakajuku, Annaka City, Gunma Prefecture (56) References 4-39412 (JP, A) JP-A-3-292416 (JP, A) JP-A-3-117725 (JP, A) (58) Fields investigated (Int. Cl. 7 , DB name) F16C 19/00 -19/56 F16C 33/30-33/66

Claims (1)

(57)【特許請求の範囲】(57) [Claims] 【請求項1】 外周面を転動面とした複数のころと、周
面をこの転動面と線接触する軌道面とした相手部材とを
備えたころ軸受に於いて、上記転動面の軸方向並びに円
周方向に亙る表面粗さが、何れも0.06μmRa以下で
あり、上記相手部材の周面の表面粗さは、軸方向に亙っ
ては0.08〜0.15μmRaであり、円周方向に亙っ
ては0.04μmRa以下である事を特徴とするころ軸
受。
1. A roller bearing comprising: a plurality of rollers having an outer peripheral surface as a rolling surface; and a mating member having a peripheral surface as a raceway surface in linear contact with the rolling surface. The surface roughness in both the axial direction and the circumferential direction is 0.06 μmRa or less, and the surface roughness of the peripheral surface of the mating member is 0.08 to 0.15 μmRa in the axial direction. A roller bearing having a diameter of 0.04 μm Ra or less in a circumferential direction.
JP21104593A 1993-08-04 1993-08-04 Roller bearing Expired - Fee Related JP3196443B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP21104593A JP3196443B2 (en) 1993-08-04 1993-08-04 Roller bearing
US08/284,977 US5456538A (en) 1993-08-04 1994-08-04 Roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP21104593A JP3196443B2 (en) 1993-08-04 1993-08-04 Roller bearing

Publications (2)

Publication Number Publication Date
JPH0742743A JPH0742743A (en) 1995-02-10
JP3196443B2 true JP3196443B2 (en) 2001-08-06

Family

ID=16599471

Family Applications (1)

Application Number Title Priority Date Filing Date
JP21104593A Expired - Fee Related JP3196443B2 (en) 1993-08-04 1993-08-04 Roller bearing

Country Status (1)

Country Link
JP (1) JP3196443B2 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997019279A1 (en) * 1995-11-21 1997-05-29 Koyo Seiko Co., Ltd. Mechanical part
DE69614369T2 (en) * 1995-11-21 2002-05-23 Koyo Seiko Co., Ltd. MECHANICAL PART
JP2005105856A (en) * 2003-09-29 2005-04-21 Ntn Corp Piston pump driving part supporting structure
CN100425850C (en) 2003-09-16 2008-10-15 Ntn株式会社 Shell-type needle roller bearing, supporting structure for compressor main shaft, and supporting structure for piston pump drive section
JP4508591B2 (en) * 2003-09-24 2010-07-21 Ntn株式会社 Compressor spindle support structure
JP2006161829A (en) * 2004-12-02 2006-06-22 Jtekt Corp One-way clutch
JP2007155021A (en) * 2005-12-06 2007-06-21 Nsk Ltd Roller bearing
JP5245889B2 (en) * 2009-02-12 2013-07-24 日本精工株式会社 Rolling guide device
JP5974532B2 (en) * 2012-02-23 2016-08-23 日本精工株式会社 Roller bearing and manufacturing method thereof
JP2014074482A (en) * 2012-10-05 2014-04-24 Nsk Ltd Rolling device and method for manufacturing the same

Also Published As

Publication number Publication date
JPH0742743A (en) 1995-02-10

Similar Documents

Publication Publication Date Title
US5456538A (en) Roller bearing
JP3196443B2 (en) Roller bearing
JP2003021145A (en) Roller bearing
JPH10196660A (en) Roller bearing
JP4730168B2 (en) Test method for radial rolling bearings
JP2017150597A (en) Rolling bearing, rolling device and manufacturing method of rolling device
JP3326915B2 (en) Roller bearing
JP2021127834A (en) Tapered roller bearing
WO1996019678A1 (en) Ball for ball bearings
US6893372B2 (en) Roller bearing, transmission using the same and differential gear
JP2003314542A (en) Tapered roller bearing
JPH09291942A (en) Radial rolling bearing
JPH0742746A (en) Roller bearing
JPH0642536A (en) Rolling roller
JPH03277823A (en) Constant velocity universal joint
JP2760626B2 (en) Constant velocity universal joint
JP2000120707A (en) Rolling bearing
JP2006112559A (en) Tapered roller bearing
JP2008019965A (en) Planetary gear device and rolling bearing
JPH07103243A (en) Rolling bearing
JP5866801B2 (en) Roller bearing
JP2965441B2 (en) Follower bearing
EP1136712A1 (en) Ball bearing and lubricating method thereof.
JP2005061495A (en) Cylindrical roller bearing
JP2002168256A (en) Rolling bearing and manufacturing method therefor

Legal Events

Date Code Title Description
FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20080608

Year of fee payment: 7

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

Free format text: PAYMENT UNTIL: 20090608

Year of fee payment: 8

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

Free format text: PAYMENT UNTIL: 20100608

Year of fee payment: 9

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

Free format text: PAYMENT UNTIL: 20100608

Year of fee payment: 9

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

Free format text: PAYMENT UNTIL: 20110608

Year of fee payment: 10

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

Free format text: PAYMENT UNTIL: 20120608

Year of fee payment: 11

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

Free format text: PAYMENT UNTIL: 20130608

Year of fee payment: 12

LAPS Cancellation because of no payment of annual fees