JP2003254338A - Conical roller bearing - Google Patents
Conical roller bearingInfo
- Publication number
- JP2003254338A JP2003254338A JP2002059213A JP2002059213A JP2003254338A JP 2003254338 A JP2003254338 A JP 2003254338A JP 2002059213 A JP2002059213 A JP 2002059213A JP 2002059213 A JP2002059213 A JP 2002059213A JP 2003254338 A JP2003254338 A JP 2003254338A
- Authority
- JP
- Japan
- Prior art keywords
- flange
- tapered roller
- bearing
- inner ring
- conical roller
- 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.)
- Granted
Links
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
-
- 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
- F16C19/36—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 a single row of rollers
- F16C19/364—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 a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
-
- 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
- F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
-
- 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
Description
【発明の詳細な説明】
【０００１】
【発明の属する技術分野】本発明は円すいころ軸受に関
する。
【０００２】
【従来の技術】円すいころ軸受においては、一般に、図
４に軸平行断面図を例示するように、内輪５１と外輪５
２の間に、転動面が円錐面の一部をなす複数の円すいこ
ろ５３を、保持器５４のポケット５４１に収容した状態
で転動自在に配置した構造を有している。
【０００３】内輪５１は、その外周に円すいころ５３の
転動面が転がり接触する円錐面の一部をなす軌道面５１
１を備えるとともに、円すいころ５３の大端面をすべり
接触のもとに案内する鍔５１２を有し、外輪５２は円す
いころ５３の転動面が転がり接触する内円錐面からなる
軌道面５２１を備えている。また、保持器５４のポケッ
ト５４１は、図５に保持器５４の正面図を示すように、
円すいころ５３を収容すべく、円すいころ５３の輪郭形
状に略沿った円錐台形の空洞によって構成されている。
【０００４】このような円すいころ軸受は、ラジアル荷
重およびスラスト荷重の双方に対して大きな負荷能力を
持ち、例えば自動車のトランスミッションやデファレン
シャル装置などに広く用いられている。
【０００５】
【発明が解決しようとする課題】ところで、以上のよう
な円すいころ軸受においては、前記した用途等において
は主として油浴潤滑法により潤滑される。また、円すい
ころ軸受においては、一般に、滑り接触する円すいころ
５３の大端面と内輪５１の鍔５１２との潤滑が軸受性能
に大きく影響する。
【０００６】しかしながら、図４に例示した従来の円す
いころ軸受によると、その形状による必然から、軸受回
転時における遠心力により、潤滑油は図４に矢印で示す
ように、軸受の小端側から軸受内部に向かう潤滑油の流
れは、円すいころ５３の側方を通って大端側に向かいつ
つ外側に、つまり外輪５２側に流れてしまい、内輪５１
の鍔５１２側には流れにくいという問題があった。
【０００７】本発明はこのような実情に鑑みてなされた
もので、軸受回転時において潤滑油が内輪の鍔側に流れ
やすく、もって円すいころと内輪の鍔との間の潤滑を良
好なものとして、高い軸受性能を発揮することのできる
円すいころ軸受の提供を目的としている。
【０００８】
【課題を解決するための手段】上記の目的を達成するた
め、本発明の円すいころ軸受は、内輪と外輪の間に、複
数の円すいころが保持器のポケットにそれぞれ収容され
た状態で転動自在に配置されてなる円すいころ軸受にお
いて、上記保持器の大端側端部に径方向外側に突出する
鍔部が形成されているとともに、上記各ポケットには、
円すいころの大端部近傍で当該円すいころとの隙間を大
きくするための凹部が形成されていることによって特徴
づけられる。
【０００９】本発明は、保持器の形状・構造を変更する
ことによって、特に油浴潤滑状態での軸受回転時におけ
る潤滑油の流れを好適に制御し、内輪の鍔と円すいころ
の大端面との接触部位に向かう潤滑油の流れを形成しよ
うとするものである。
【００１０】すわなち、保持器の大端側の端部に径方向
外側に突出する鍔部形成することにより、軸受回転時に
遠心力によって円すいころの側方を通って外輪側に流れ
出る潤滑油がせき止められ、各ポケットに形成した凹部
を通って内輪の鍔側に流れ出る。従って、本発明による
と、軸受回転時に内輪の鍔と円すいころの大端面との滑
り接触部位に、従来に比して多量の潤滑油を供給するこ
とができ、これらの間の潤滑を良好なものとすることが
できる。
【００１１】
【発明の実施の形態】以下、図面を参照しつつ本発明の
実施の形態について説明する。図１は本発明の実施の形
態の軸平行断面図であり、図２はその保持器４の正面図
であって、図３はポケット４１内に円すいころ３を収容
した状態を正面から見た図である。
【００１２】内輪１と外輪２の間に、複数の円すいころ
３がそれぞれ保持器４のポケット４１に収容されること
により周方向に一定の間隔を開けた状態で転動自在に配
置されている。
【００１３】内輪１、外輪２および円すいころ３は従来
の円すいころ軸受と同等であって、内輪１には円すいこ
ろ３の外周の転動面が転がり接触する円錐面の一部をな
す軌道面１１がその外周に形成されているとともに、そ
の軌道面１１の大端側には円すいころ３の大端面を滑り
接触のもとに案内する鍔１２が形成されている。また、
外輪２にはその内周に円すいころ３が転がり接触する内
円錐面の一部をなす軌道面２１が形成されている。
【００１４】保持器４はこの例においてプレス製の打ち
抜き保持器であって、この保持器４には、その大端側の
端部に外側に突出するように折り曲げられてなる鍔部４
２が形成されている。この鍔部４２の先端は、組立状態
において外輪２の端部に対して若干の隙間を介して接近
している。
【００１５】また、保持器４の各ポケット４１は、円す
いころ３を収容すべく当該円すいころ３の輪郭形状に略
等しい円錐台形の空洞を基本形状としているが、そのポ
ケット４１の大端側の端部両側に凹部４１ａが形成され
ており、この凹部４１ａの形成位置において円すいころ
３との間に相当の隙間が形成されている。
【００１６】以上の本発明の実施の形態によると、油浴
潤滑で用いたとき、軸受の小端側、つまり図１において
左側から流れてくる潤滑油は、軸受の回転により各円す
いころ３の側方を通って大端側へと流れつつ、遠心力に
よって外輪２側に流れ出ようとするが、図１に矢印で示
すように、保持器４の鍔部４２の存在によりその流れは
せき止められる。そして、一部の潤滑油はこの鍔部４２
の先端と外輪２との間を通って軸受外に流れるが、他の
殆どの潤滑油は、各ポケット４１に形成されて円すいこ
ろ３の外周面との間に隙間を形成している凹部４１ａを
通って内輪１の鍔１２側に向けて流れる。
【００１７】従って、本発明の実施の形態によれば、内
輪１の鍔１２と円すいころ３の大端面との間に従来に比
して多量の潤滑油が供給されることになり、これらの間
の潤滑性を著しく向上させることができる。
【００１８】また、以上の実施の形態において、保持器
４の鍔部４１の先端と外輪２との間の隙間と、各ポケッ
ト４１の凹部４１ａによる円すいころ３との間の隙間の
相対的な大きさを変化させることによって、軸受内部に
流れてくる潤滑油のうち、内輪１の鍔１２側へ流れる潤
滑油の量を適宜に変化させることができる。
【００１９】なお、以上の実施の形態においては、保持
器４の各ポケット４１の大端側の端部の両側に凹部４１
ａを設けて潤滑油の通路を形成したが、各ポケット４１
ａに形成する凹部４１ａの数や形状、並びに位置につい
ては特に限定されることなく、要は各円すいころ３の大
端部の近傍に、当該円すいころ３との間の隙間を大きく
することのできる任意形状、任意数の凹部４１ａが形成
されていればよい。
【００２０】また、以上の実施の形態においては、保持
器４としてプレス製の打ち抜き保持器を用いたが、本発
明はこれに限定されることなく、揉み抜き保持器をはじ
めとして他の型式の保持器であってもよく、また、樹脂
製の保持器にも等しく適用し得ることは勿論である。
【００２１】
【発明の効果】以上のように、本発明によれば、円すい
ころ軸受の保持器の大端側の端部に外輪側に突出する鍔
部を形成するとともに、その保持器の各ポケットには、
円すいころの大端部近傍で当該円すいころとの隙間を大
きくするための凹部を形成しているので、軸受の回転時
に、軸受内に流れて各円すいころの間を流れつつ遠心力
により外側に流れようとする潤滑油は、保持器の鍔部に
よりせき止められ、各ポケットの凹部と円すいころの間
を通って内輪の鍔側に流れることになり、従来の円すい
ころ軸受に比して内輪の鍔と円すいころの大端面との間
に供給される潤滑油量を多くすることができ、これらの
間の潤滑性を向上させることができる。
【００２２】その結果、本発明によると、内輪の鍔と円
すいころの大端面との間の耐焼き付き性の向上と、回転
トルクの軽減を達成することができ、円すいころ軸受と
しての性能を最大限に発揮することが可能となる。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tapered roller bearing. 2. Description of the Related Art In a tapered roller bearing, an inner race 51 and an outer race 5 are generally provided as shown in FIG.
2, a plurality of tapered rollers 53 whose rolling surfaces form a part of a conical surface are arranged so as to roll freely while being accommodated in pockets 541 of a retainer 54. [0003] The inner ring 51 has a raceway surface 51 which forms a part of a conical surface with which the rolling surface of the tapered roller 53 is in rolling contact with its outer periphery.
1 and a flange 512 for guiding the large end face of the tapered roller 53 under sliding contact, and the outer race 52 is provided with a raceway surface 521 formed of an inner conical surface with which the rolling surface of the tapered roller 53 comes into rolling contact. ing. The pocket 541 of the retainer 54 is, as shown in FIG.
In order to accommodate the tapered roller 53, the tapered roller 53 is formed by a truncated cone-shaped cavity substantially along the contour shape of the tapered roller 53. [0004] Such a tapered roller bearing has a large load capacity against both a radial load and a thrust load, and is widely used in, for example, an automobile transmission and a differential device. [0005] Incidentally, the tapered roller bearing described above is mainly lubricated by an oil bath lubrication method in the above-mentioned applications and the like. In addition, in the tapered roller bearing, generally, lubrication between the large end surface of the tapered roller 53 and the flange 512 of the inner ring 51 that come into sliding contact greatly affects the bearing performance. However, according to the conventional tapered roller bearing illustrated in FIG. 4, the lubricating oil flows from the small end side of the bearing as shown by the arrow in FIG. The flow of the lubricating oil toward the inside of the bearing flows outward toward the large end through the side of the tapered rollers 53, that is, flows toward the outer ring 52 side.
There was a problem that it was difficult to flow on the flange 512 side. The present invention has been made in view of such circumstances, and it is intended that lubricating oil easily flows to the flange side of the inner ring during rotation of the bearing, so that lubrication between the tapered rollers and the flange of the inner ring is improved. The purpose of the present invention is to provide a tapered roller bearing capable of exhibiting high bearing performance. In order to achieve the above object, a tapered roller bearing according to the present invention has a plurality of tapered rollers housed in a pocket of a retainer between an inner ring and an outer ring. In the tapered roller bearing which is arranged to be able to roll freely, a flange portion projecting radially outward is formed at a large end side of the retainer, and each pocket is
It is characterized by the fact that a recess is formed near the large end of the tapered roller to increase the gap with the tapered roller. According to the present invention, by changing the shape and structure of the cage, the flow of lubricating oil is preferably controlled particularly when the bearing is rotated in an oil bath lubrication state, and the inner ring flange and the large end face of the tapered roller are provided. Is intended to form a flow of the lubricating oil toward the contact area. In other words, by forming a flange projecting radially outward at the large end of the cage, lubricating oil flowing toward the outer ring through the side of the tapered roller due to centrifugal force when the bearing rotates. It is caught and flows to the flange side of the inner ring through the recess formed in each pocket. Therefore, according to the present invention, a large amount of lubricating oil can be supplied to the sliding contact portion between the flange of the inner ring and the large end surface of the tapered roller when the bearing rotates, and lubrication between them can be improved. Things. Embodiments of the present invention will be described below with reference to the drawings. 1 is an axially parallel sectional view of an embodiment of the present invention, FIG. 2 is a front view of a retainer 4, and FIG. 3 is a front view of a state in which a tapered roller 3 is accommodated in a pocket 41. FIG. A plurality of tapered rollers 3 are respectively accommodated in pockets 41 of a retainer 4 between the inner ring 1 and the outer ring 2 so as to be rotatable with a certain interval in the circumferential direction. . The inner ring 1, the outer ring 2 and the tapered roller 3 are equivalent to a conventional tapered roller bearing. The inner ring 1 has a raceway surface which forms a part of a conical surface with which the rolling surface on the outer periphery of the tapered roller 3 makes rolling contact. 11 is formed on the outer periphery, and a large end of the raceway surface 11 is formed with a flange 12 for guiding the large end surface of the tapered roller 3 under sliding contact. Also,
A raceway surface 21 which forms a part of an inner conical surface with which the tapered rollers 3 are in rolling contact with the inner periphery of the outer ring 2 is formed. The retainer 4 is a punched retainer in this example. The retainer 4 has a flange 4 formed at its large end so as to project outward.
2 are formed. The distal end of the flange 42 is close to the end of the outer race 2 with a slight gap in the assembled state. Each pocket 41 of the retainer 4 has a basic shape of a truncated cone substantially equal to the contour shape of the tapered roller 3 for accommodating the tapered roller 3. A concave portion 41a is formed on both sides of the end portion, and a considerable gap is formed between the concave portion 41a and the tapered roller 3 at the position where the concave portion 41a is formed. According to the above embodiment of the present invention, when used in oil bath lubrication, lubricating oil flowing from the small end side of the bearing, that is, from the left side in FIG. While flowing toward the large end through the side, the centrifugal force tends to flow to the outer ring 2 side, but as shown by the arrow in FIG. 1, the flow is blocked by the presence of the flange 42 of the retainer 4. . Some of the lubricating oil is
Flows through the space between the tip of the outer ring 2 and the outer ring 2, but most of the other lubricating oil is formed in each pocket 41 and forms a clearance between the outer peripheral surface of the tapered roller 3 and the recess 41 a Through the inner ring 1 toward the flange 12 side. Therefore, according to the embodiment of the present invention, a larger amount of lubricating oil is supplied between the flange 12 of the inner ring 1 and the large end face of the tapered roller 3 than in the prior art. The lubricity between the two can be significantly improved. In the above embodiment, the relative clearance between the gap between the tip of the flange 41 of the retainer 4 and the outer ring 2 and the tapered roller 3 formed by the concave portion 41a of each pocket 41. By changing the size, the amount of the lubricating oil flowing toward the flange 12 of the inner ring 1 among the lubricating oil flowing into the bearing can be appropriately changed. In the above embodiment, the concave portions 41 are provided on both sides of the large end of each pocket 41 of the retainer 4.
a was provided to form a passage for the lubricating oil.
The number, shape, and position of the concave portions 41a formed in a are not particularly limited. In short, it is important to increase the gap between the tapered rollers 3 near the large end of each tapered roller 3. It is only necessary that any possible shape and any number of concave portions 41a be formed. Further, in the above-described embodiment, a punched and made retainer is used as the retainer 4. However, the present invention is not limited to this. It is needless to say that a retainer may be used, and the present invention is equally applicable to a retainer made of resin. As described above, according to the present invention, a flange protruding toward the outer ring is formed at the large end of the tapered roller bearing retainer. In the pocket,
A concave portion is formed in the vicinity of the large end of the tapered roller to increase the gap between the tapered roller, so that when the bearing rotates, it flows into the bearing, flows between the tapered rollers, and moves outward due to centrifugal force. The lubricating oil that is about to flow is dammed by the flange of the retainer, flows between the recess of each pocket and the tapered roller, and flows to the flange side of the inner ring. The amount of lubricating oil supplied between the flange and the large end surface of the tapered rollers can be increased, and the lubricity between them can be improved. As a result, according to the present invention, the seizure resistance between the flange of the inner ring and the large end face of the tapered roller and the reduction of the rotating torque can be achieved, and the performance as a tapered roller bearing is maximized. It is possible to demonstrate to the limit.
【図面の簡単な説明】
【図１】本発明の実施の形態の軸平行断面図である。
【図２】本発明の実施の形態の保持器４の正面図であ
る。
【図３】本発明の実施の形態における保持器４のポケッ
ト４１を、円すいころ３を収容した状態で見た正面図で
ある。
【図４】従来の円すいころ軸受の構成例を示す軸平行断
面図である。
【図５】図４の従来の円すいころ軸受の保持器５４の正
面図である。
【符号の説明】
１ 内輪
１１ 軌道面
１２ 鍔
２ 外輪
３ 円すいころ
４ 保持器
４１ ポケット
４１ａ 凹部
４２ 鍔部BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an axially parallel sectional view of an embodiment of the present invention. FIG. 2 is a front view of the retainer 4 according to the embodiment of the present invention. FIG. 3 is a front view of the pocket 41 of the retainer 4 according to the embodiment of the present invention when the tapered roller 3 is accommodated. FIG. 4 is an axially parallel sectional view showing a configuration example of a conventional tapered roller bearing. FIG. 5 is a front view of the conventional tapered roller bearing retainer 54 of FIG. [Description of Signs] 1 Inner ring 11 Track surface 12 Flange 2 Outer ring 3 Tapered roller 4 Cage 41 Pocket 41a Depression 42 Flange
Claims (1)
保持器のポケットにそれぞれ収容された状態で転動自在
に配置されてなる円すいころ軸受において、 上記保持器の大端側端部に径方向外側に突出する鍔部が
形成されているとともに、上記各ポケットには、円すい
ころの大端部近傍で当該円すいころとの隙間を大きくす
るための凹部が形成されていることを特徴とする円すい
ころ軸受。Claims: 1. A tapered roller bearing comprising a plurality of tapered rollers which are rotatably arranged between an inner ring and an outer ring while being housed in respective pockets of the cage. A flange protruding radially outward is formed at the large end of the pocket, and a recess is formed in each of the pockets near the large end of the tapered roller to increase the gap between the tapered roller and the pocket. Tapered roller bearing characterized by being made.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002059213A JP4126529B2 (en) | 2002-03-05 | 2002-03-05 | Tapered roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002059213A JP4126529B2 (en) | 2002-03-05 | 2002-03-05 | Tapered roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003254338A true JP2003254338A (en) | 2003-09-10 |
| JP4126529B2 JP4126529B2 (en) | 2008-07-30 |
Family
ID=28668962
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002059213A Expired - Fee Related JP4126529B2 (en) | 2002-03-05 | 2002-03-05 | Tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4126529B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008015829A1 (en) * | 2006-08-01 | 2008-02-07 | Ntn Corporation | Tapered roller bearing |
| WO2008087926A1 (en) * | 2007-01-15 | 2008-07-24 | Jtekt Corporation | Conical roller bearing |
| US7645074B2 (en) | 2005-04-28 | 2010-01-12 | Jtekt Corporation | Fluid-lubricated type tapered roller bearing device and vehicle pinion shaft supporting assembly |
| US7722257B2 (en) | 2006-03-30 | 2010-05-25 | Jtekt Corporation | Roller bearing cage and tapered roller bearing |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012064939A2 (en) | 2010-11-10 | 2012-05-18 | Nanoh2O, Inc. | Improved hybrid tfc ro membranes with non-metallic additives |
| CN104595363A (en) * | 2013-10-31 | 2015-05-06 | 刘发扬 | Novel centrifugal self-lubricating tapered roller bearing retainer |
-
2002
- 2002-03-05 JP JP2002059213A patent/JP4126529B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7645074B2 (en) | 2005-04-28 | 2010-01-12 | Jtekt Corporation | Fluid-lubricated type tapered roller bearing device and vehicle pinion shaft supporting assembly |
| US7722257B2 (en) | 2006-03-30 | 2010-05-25 | Jtekt Corporation | Roller bearing cage and tapered roller bearing |
| WO2008015829A1 (en) * | 2006-08-01 | 2008-02-07 | Ntn Corporation | Tapered roller bearing |
| JP2008038927A (en) * | 2006-08-01 | 2008-02-21 | Ntn Corp | Tapered roller bearing |
| US8152383B2 (en) * | 2006-08-01 | 2012-04-10 | Ntn Corporation | Tapered roller bearing |
| WO2008087926A1 (en) * | 2007-01-15 | 2008-07-24 | Jtekt Corporation | Conical roller bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4126529B2 (en) | 2008-07-30 |
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