JPH11270553A - Double row tapered roller bearing - Google Patents
Double row tapered roller bearingInfo
- Publication number
- JPH11270553A JPH11270553A JP7261198A JP7261198A JPH11270553A JP H11270553 A JPH11270553 A JP H11270553A JP 7261198 A JP7261198 A JP 7261198A JP 7261198 A JP7261198 A JP 7261198A JP H11270553 A JPH11270553 A JP H11270553A
- Authority
- JP
- Japan
- Prior art keywords
- tapered roller
- crowning
- raceway surface
- inner ring
- double row
- 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
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は複列円すいころ軸
受に関するもので、より詳しくは、クラウニング形状を
改良することによってころのスキューを防止し、軸受の
寿命を向上させたものである。ここに、ころのスキュー
とは、ころが正規の自転軸に対して傾くことをいう。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double-row tapered roller bearing, and more particularly to an improved crowning shape for preventing roller skew and extending the life of the bearing. Here, the skew of the rollers means that the rollers are inclined with respect to the normal rotation axis.
【０００２】[0002]
【従来の技術】クラウニングとは、軌道輪ところとの接
触部に生ずる集中荷重（エッジロード）を防ぐことを主
な目的として軌道又はころの母線にごくわずかに曲率を
もたせることをいい、軸受の技術分野においてはよく知
られている。たとえば自動車のアクスルユニット用円す
いころ軸受は、高モーメント負荷による軌道面のエッジ
ロードを避けるため、軌道面および円すいころの転動面
にクラウニングを設けている。2. Description of the Related Art Crowning refers to giving a track or a roller bus bar a very slight curvature mainly for the purpose of preventing a concentrated load (edge load) generated at a contact portion with a raceway. It is well known in the art. For example, in a tapered roller bearing for an axle unit of an automobile, a crowning is provided on a raceway surface and a rolling surface of a tapered roller in order to avoid an edge load on a raceway surface due to a high moment load.
【０００３】図３（Ａ）に示すように、特に面圧の高い
内輪の軌道面（母線長さを符号Ｌで示す。）には、中央
部のクラウニング（Ｃ）に加えて、さらに両端部にもカ
ットクラウニング（ＣＬ，ＣＳ）を設けてある。図３
（Ａ）において、大径側のカットクラウニング（ＣＬ）
は、幅をＷＬ、クラウニング量をＨＬで表してあり、小
径側のカットクラウニング（ＣＳ）は、幅をＷＳ、クラ
ウニング量をＨＳで表してある。そして、面圧分布を考
慮して、小径側のカットクラウニング（ＣＳ）に比べて
大径側のカットクラウニング（ＣＳ）のクラウニング量
を大きく設定するのが一般的である（ＨＬ＞ＨＳ）。こ
のため、円すいころの転動面と内輪の軌道面との接触点
（Ｐｉ）および円すいころの転動面と外輪の軌道面との
接触点（Ｐｏ）が、符号ｅで示すように、円すいころの
軸線（Ｘ−Ｘ）方向にずれる。言い換えれば、外輪の軌
道面と円すいころの転動面との接触点（Ｐｏ）が円すい
ころの転動面の中心線上に位置するのに対し、内輪の軌
道面と円すいころの転動面との接触点（Ｐｉ）は、円す
いころの転動面の中心線よりも円すいころの小径側に位
置している。なお、接触点（Ｐｉ）は、内輪の軌道面に
おける中央部のクラウニング（Ｃ）の中心線上に位置
し、この意味でクラウニング（Ｃ）は対称である。これ
に対して両端部のカットクラウニング（ＣＬ，ＣＳ）は
非対称である。[0003] As shown in FIG. 3 (A), the raceway surface of the inner ring (particularly, the length of the bus is denoted by L) having a particularly high surface pressure, in addition to the crowning (C) at the center, and both ends. Is also provided with cut crowning (CL, CS). FIG.
In (A), the cut crowning on the large diameter side (CL)
Represents the width by WL and the crowning amount by HL, and the cut crowning (CS) on the smaller diameter side represents the width by WS and the crowning amount by HS. In general, the crowning amount of the large-diameter cut crowning (CS) is set larger than the small-diameter cut crowning (CS) in consideration of the surface pressure distribution (HL> HS). For this reason, the point of contact (Pi) between the rolling surface of the tapered roller and the raceway surface of the inner ring and the point of contact (Po) between the rolling surface of the tapered roller and the raceway surface of the outer ring are indicated by the reference numeral e. The roller is shifted in the direction of the axis (XX). In other words, the contact point (Po) between the raceway surface of the outer ring and the rolling surface of the tapered roller is located on the center line of the rolling surface of the tapered roller, whereas the contact point (Po) of the raceway surface of the inner ring and the rolling surface of the tapered roller are different. Is located on the smaller diameter side of the tapered roller than the center line of the rolling surface of the tapered roller. The contact point (Pi) is located on the center line of the crowning (C) at the center of the raceway surface of the inner ring, and in this sense, the crowning (C) is symmetric. In contrast, the cut crowning (CL, CS) at both ends is asymmetric.
【０００４】[0004]
【発明が解決しようとする課題】上述の内・外輪の軌道
面と円すいころの転動面との接触点（Ｐｉ，Ｐｏ）のズ
レは円すいころのスキューの原因となる。そこで、この
発明の目的は、軌道面および円すいころの転動面にクラ
ウニングを設けた複列円すいころ軸受において、円すい
ころのスキューを防止して軸受の寿命を一層向上させる
ことにある。The deviation of the contact points (Pi, Po) between the raceway surfaces of the inner and outer races and the rolling surface of the tapered rollers causes skew of the tapered rollers. SUMMARY OF THE INVENTION An object of the present invention is to provide a double-row tapered roller bearing in which a raceway surface and a rolling surface of a tapered roller are provided with crownings to prevent skew of the tapered roller and further improve the life of the bearing.
【０００５】[0005]
【課題を解決するための手段】この発明は、外輪の軌道
面のクラウニング頂点を小径側に移動させ、内・外輪の
軌道面と円すいころの転動面との接触点の円すいころの
軸線方向における位置を一致させることによって課題を
解決したものである。According to the present invention, the crowning vertex of the raceway surface of the outer ring is moved to the small diameter side, and the axial direction of the tapered roller at the point of contact between the raceway surface of the inner and outer rings and the rolling surface of the tapered roller. The problem has been solved by matching the positions in.
【０００６】すなわち、請求項１の発明は、内輪の軌道
面の中央部にクラウニングを形成するとともに両端部に
非対称のカットクラウニングを形成し、外輪の軌道面に
フルクラウニングを形成し、かつ、円すいころの転動面
にフルクラウニングを形成してなり、円すいころと内輪
軌道面の接触点と、円すいころと外輪軌道面の接触点と
を、円すいころの軸線方向で一致させたことを特徴とす
る。That is, according to the first aspect of the present invention, the crowning is formed at the center of the raceway surface of the inner ring, the asymmetrical cut crowning is formed at both ends, the full crowning is formed on the raceway surface of the outer ring, and the cone is formed. Full crowning is formed on the rolling surface of the roller, and the point of contact between the tapered roller and the inner ring raceway surface and the point of contact between the tapered roller and the outer ring raceway surface coincide in the axial direction of the tapered roller. I do.
【０００７】このような構成を採用したことによって、
軸受回転時に円すいころが内輪軌道面および外輪軌道面
から受ける力の作用点が円すいころの軸線すなわち自転
軸上で一致し、しかも、円すいころの軸線（自転軸）か
ら外輪軌道面との接触点および内輪軌道面との接触点ま
での距離（半径）が等しくなるため、円すいころの軸線
を傾けようとするモーメントが作用せず、ころのスキュ
ーが生じにくくなる。By adopting such a configuration,
The points of action of the forces received by the tapered rollers from the inner ring raceway surface and the outer ring raceway during bearing rotation coincide on the axis of the tapered roller, that is, on the rotation axis, and at the point of contact between the tapered roller axis (rotation axis) and the outer ring raceway surface. In addition, since the distance (radius) to the contact point with the inner raceway surface becomes equal, a moment for tilting the axis of the tapered roller does not act, and the skew of the roller hardly occurs.
【０００８】非対称のカットクラウニングというとき
は、クラウニングの幅および／または量に関して、小径
側と大径側とで異なることを意味する。実際には当該複
列円すいころ軸受の用途や設計仕様等に応じて定められ
るものであるが、複列円すいころ軸受の場合、内輪の大
径側のカットクラウニングのクラウニング量を小径側よ
りも大きく設定するのが一般的である。[0008] Asymmetric cut crowning means that the width and / or amount of crowning differs between the small diameter side and the large diameter side. Actually, it is determined according to the application and design specifications of the double row tapered roller bearing, but in the case of double row tapered roller bearing, the crowning amount of the cut crowning on the large diameter side of the inner ring is larger than that of the small diameter side. It is common to set.
【０００９】内輪の軌道面の両端部に非対称のカットク
ラウニングを配置することから、中央部のクラウニング
の母線方向長さの中心線は、軌道面全体の母線方向長さ
の中心線とは一致しないこととなるが、中央部のクラウ
ニングの全域にわたって荷重を分布させるうえで、円す
いころの転動面と内輪の軌道面との接触点を中央部のク
ラウニングの母線方向長さの中心線上に配置するのが好
ましい。Since the asymmetrical cut crowning is arranged at both ends of the raceway surface of the inner race, the center line of the central portion of the crowning in the generatrix direction does not coincide with the centerline of the entire raceway surface in the generatrix direction. In other words, in order to distribute the load over the entire area of the central crowning, the contact point between the rolling surface of the tapered rollers and the raceway surface of the inner ring is arranged on the center line of the central crowning length in the direction of the generatrix. Is preferred.
【００１０】[0010]
【発明の実施の形態】図１に示す複列円すいころ軸受
（１０）は、それぞれ軌道面（２２）を備えた一対の内
輪（２０）と、複列の軌道面（３２）を備えた複列外輪
（３０）と、内・外輪（２０，３０）の軌道面（２２，
３２）間に転動自在に組み込まれた複列の円すいころ
（４０）と、各列の円すいころ（４０）を円周方向に等
間隔に保つための保持器（５０）と、内・外輪（２０，
３０）間に形成された軸受空間を密封するためのシール
（６０）とで構成されている。DESCRIPTION OF THE PREFERRED EMBODIMENTS A double row tapered roller bearing (10) shown in FIG. 1 has a pair of inner races (20) each having a raceway surface (22) and a double row tapered roller bearing (32) having a double row raceway surface (32). Row outer races (30) and raceway surfaces (22, 22) of inner and outer races (20, 30)
32) Double row tapered rollers (40) rotatably mounted between them, cages (50) for keeping the tapered rollers (40) in each row at equal intervals in the circumferential direction, and inner and outer rings (20,
30) and a seal (60) for sealing the bearing space formed therebetween.
【００１１】図２（Ａ）に示すように、円すいころ（４
０）の転動面（４２）には対称なクラウニングを設けて
あり、大端面（４４）は内輪（２０）の大つば（２４）
によって接触案内される。なお、図２（Ａ）は図１の一
部を拡大したものであるが、理解を容易にするためクラ
ウニング部分を誇張したものであり、また、内輪（２
０）の軌道面（２２）のクラウニング寸法に関しては図
３と変わるところがないので符号を省略してある。As shown in FIG. 2A, tapered rollers (4
The rolling surface (42) of (0) is provided with symmetrical crowning, and the large end surface (44) is a large collar (24) of the inner ring (20).
Guided by contact. Although FIG. 2A is a partially enlarged view of FIG. 1, the crowning portion is exaggerated for easy understanding, and the inner ring (2
The crowning dimension of the raceway surface (22) of (0) is not different from that of FIG.
【００１２】内輪（２０）は軸方向の両端に大つば（２
４）と小つば（２６）を有し、これらのつば（２４，２
６）の間に軌道みぞ（２８）が画成されている。軌道み
ぞ（２８）の底面にあたる軌道面（２２）は、その母線
長さの中央部のクラウニング（Ｃ）と、両端部のカット
クラウニング（ＣＬ，ＣＳ）とで構成される。図３に関
連して既に述べたとおり、大径側のカットクラウニング
（ＣＬ）については幅をＷＬ、クラウニング量をＨＬと
し、小径側のカットクラウニング（ＣＳ）については、
幅をＷＳ、クラウニング量をＨＳとする。図２（Ａ）お
よび図３（Ａ）から明らかなように、大径側のカットク
ラウニング（ＣＬ）の方が小径側のカットクラウニング
（ＣＳ）よりも幅、クラウニング量共に大きく設定され
ている（ＷＬ＞ＷＳ，ＨＬ＞ＨＳ）。符号Ｐｉは軌道面
（２２）と円すいころ（４０）との接触点を表し、中央
部のクラウニング（Ｃ）の母線方向長さの中心線上に位
置する。The inner ring (20) has large collars (2) at both ends in the axial direction.
4) and a small brim (26).
A track groove (28) is defined during 6). The raceway surface (22), which is the bottom surface of the raceway groove (28), is constituted by a crowning (C) at the center of the generatrix length and cut crownings (CL, CS) at both ends. As described above with reference to FIG. 3, the width of the large-diameter cut crown (CL) is WL, the amount of the crown is HL, and the small-diameter cut crown (CS) is
The width is WS, and the crowning amount is HS. As is clear from FIGS. 2A and 3A, both the width and the crowning amount of the cut crowning (CL) on the large diameter side are set to be larger than those of the cut crowning (CS) on the small diameter side. WL> WS, HL> HS). Reference symbol Pi represents a contact point between the raceway surface (22) and the tapered roller (40), and is located on the center line of the central portion of the crowning (C) in the generatrix direction.
【００１３】外輪（３０）の軌道面（３２）にもクラウ
ニングを設けてあるが、クラウニングの頂点すなわち円
すいころ（４０）との接触点を符号Ｐｏで表してある。
この接触点（Ｐｏ）は、内輪（２０）の軌道面（２２）
と円すいころ（４０）の転動面（４２）との接触点（Ｐ
ｉ）を通り、円すいころ（４０）の軸線（Ｘ−Ｘ）に垂
直な直線上に位置する。言い換えるならば、図３の場合
と比べて、接触点（Ｐｉ）を円すいころ（４０）の軸線
（Ｘ−Ｘ）に沿って小径側に移動させたものといえる。The raceway surface (32) of the outer race (30) is also provided with a crowning, and the vertex of the crowning, that is, the point of contact with the tapered roller (40) is denoted by Po.
This contact point (Po) is determined by the raceway surface (22) of the inner ring (20).
The point of contact (P) between the roller and the rolling surface (42) of the tapered roller (40)
It passes through i) and is located on a straight line perpendicular to the axis (XX) of the tapered roller (40). In other words, it can be said that the contact point (Pi) is moved to the smaller diameter side along the axis (XX) of the tapered roller (40) as compared with the case of FIG.
【００１４】両接触点（Ｐｉ，Ｐｏ）の円すいころ（４
０）の軸線（Ｘ−Ｘ）方向における位置が一致している
ため、図２（Ｂ）に示すように軸受回転時に円すいころ
（４０）が内輪（２０）および外輪（３０）から受ける
力の作用点が一致し、円すいころ（４０）の軸線（Ｘ−
Ｘ）から各接触点（Ｐｉ，Ｐｏ）までの距離（半径）も
等しくなる（図２（Ｃ）参照）。したがって、円すいこ
ろ（４０）の軸線（自転軸）を傾けようとするモーメン
トが作用せず、円すいころ（４０）が正規の軸線を維持
してスキューを起こすことなく転動することができる。Tapered rollers (4) at both contact points (Pi, Po)
2), the positions of the tapered rollers (40) received from the inner ring (20) and the outer ring (30) during rotation of the bearing as shown in FIG. 2 (B). The action points coincide, and the axis of the tapered roller (40) (X-
The distance (radius) from X) to each contact point (Pi, Po) is also equal (see FIG. 2C). Therefore, no moment acts to tilt the axis (rotation axis) of the tapered roller (40), and the tapered roller (40) can maintain the normal axis and roll without causing skew.
【００１５】[0015]
【発明の効果】以上説明したように、この発明によれ
ば、円すいころの軸線方向において、内輪の軌道面と円
すいころの転動面との接触点の位置と、外輪の軌道面と
円すいころの転動面との接触点とを一致させたことによ
り、軸受回転時に円すいころが内輪の軌道面および外輪
の軌道面から受ける力の作用点が円すいころの軸線（自
転軸）方向で一致し、しかも、円すいころの軸線（自転
軸）から内輪の軌道面および外輪の軌道面との接触点ま
での距離（半径）が等しくなる。したがって、従来のよ
うに軸受回転時に円すいころの軸線を傾けようとするモ
ーメントが作用することはない。その結果、円すいころ
のスキューが生じにくくなり、軸受寿命の一層の向上が
図られる。As described above, according to the present invention, the position of the contact point between the raceway surface of the inner ring and the rolling surface of the tapered roller and the raceway surface of the outer ring and the tapered roller in the axial direction of the tapered roller. The point of application of the force that the tapered roller receives from the raceway surface of the inner ring and the raceway surface of the outer ring during bearing rotation matches in the direction of the axis of the tapered roller (rotation axis). Moreover, the distance (radius) from the tapered roller axis (rotation axis) to the contact point between the raceway surface of the inner ring and the raceway surface of the outer ring becomes equal. Therefore, unlike the related art, a moment for tilting the tapered roller axis during rotation of the bearing does not act. As a result, skew of the tapered rollers hardly occurs, and the life of the bearing is further improved.
【図１】複列円すいころ軸受の半断面図である。FIG. 1 is a half sectional view of a double-row tapered roller bearing.
【図２】（Ａ）は図１の部分拡大図、（Ｂ）は（Ａ）に
おける円すいころの平面略図、（Ｃ）は（Ａ）における
円すいころの横断面略図である。2A is a partially enlarged view of FIG. 1, FIG. 2B is a schematic plan view of the tapered roller in FIG. 2A, and FIG. 2C is a schematic cross-sectional view of the tapered roller in FIG.
【図３】（Ａ）は図２（Ａ）と類似の部分拡大図、
（Ｂ）は（Ａ）における円すいころの平面略図、（Ｃ）
は（Ａ）における円すいころの横断面略図である。FIG. 3 (A) is a partially enlarged view similar to FIG. 2 (A),
(B) is a schematic plan view of the tapered rollers in (A), (C)
1 is a schematic cross-sectional view of a tapered roller in (A).
２０ 内輪 ２２ 軌道面 Ｃ 中央部のクラウニング ＣS 小径側のカットクラウニング ＣL 大径側のカットクラウニング Ｐｉ 接触点（内輪軌道面と円すいころの） Ｐｏ 接触点（外輪軌道面と円すいころの） ２４ 大つば ２６ 小つば ２８ 軌道みぞ ３０ 外輪 ３２ 軌道面 ４０ 円すいころ ４２ 転動面 ４４ 大端面 Ｘ−Ｘ 円すいころの軸線（自転軸） ５０ 保持器 ６０ シール Reference Signs List 20 inner ring 22 raceway surface C crowning at center part CS s cut crowning at small diameter side CL cut crowning at large diameter side Pi contact point (of inner ring raceway surface and tapered roller) Po contact point (of outer ring raceway surface and tapered roller) 24 large collar 26 small brim 28 raceway groove 30 outer ring 32 raceway surface 40 tapered roller 42 rolling surface 44 large end surface XX axis of tapered roller (rotation axis) 50 retainer 60 seal
Claims (3)
形成するとともに両端部に非対称のカットクラウニング
を形成し、外輪の軌道面にフルクラウニングを形成し、
かつ、円すいころの転動面にフルクラウニングを形成し
てなり、円すいころの転動面と内輪の軌道面との接触点
と、円すいころの転動面と外輪の軌道面との接触点を、
円すいころの軸線方向で一致させたことを特徴とする複
列円すいころ軸受。1. A crowning is formed at a central portion of a raceway surface of an inner ring, an asymmetrical cut crowning is formed at both ends, and a full crowning is formed on a raceway surface of an outer ring.
Also, full crowning is formed on the rolling surface of the tapered roller, and the contact point between the rolling surface of the tapered roller and the raceway surface of the inner ring, and the contact point between the rolling surface of the tapered roller and the raceway surface of the outer ring are formed. ,
Double row tapered roller bearings characterized in that they are aligned in the axial direction of the tapered rollers.
ラウニング量が小径側のカットクラウニングのクラウニ
ング量よりも大きいことを特徴とする請求項１の複列円
すいころ軸受。2. The double row tapered roller bearing according to claim 1, wherein the crowning amount of the cut crowning on the large diameter side of the inner ring is larger than the crowning amount of the cut crowning on the small diameter side.
接触点を、内輪の軌道面における中央部のクラウニング
の母線方向長さの中心線上に配置したことを特徴とする
請求項１の複列円すいころ軸受。3. A contact point between a rolling surface of a tapered roller and a raceway surface of an outer ring is arranged on a center line of a length in a generatrix direction of a central portion of a raceway surface of an inner ring. Double row tapered roller bearing.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07261198A JP4040160B2 (en) | 1998-03-20 | 1998-03-20 | Double row tapered roller bearing |
| US09/270,529 US6126322A (en) | 1998-03-20 | 1999-03-17 | Vehicle wheel supporting structure |
| FR9903437A FR2776237B1 (en) | 1998-03-20 | 1999-03-19 | VEHICLE WHEEL SUPPORT STRUCTURE |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07261198A JP4040160B2 (en) | 1998-03-20 | 1998-03-20 | Double row tapered roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11270553A true JPH11270553A (en) | 1999-10-05 |
| JP4040160B2 JP4040160B2 (en) | 2008-01-30 |
Family
ID=13494373
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP07261198A Expired - Lifetime JP4040160B2 (en) | 1998-03-20 | 1998-03-20 | Double row tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4040160B2 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002089553A (en) * | 2000-09-12 | 2002-03-27 | Nsk Ltd | Rolling bearing for continuous casting machine |
| WO2007058112A1 (en) * | 2005-11-16 | 2007-05-24 | Ntn Corporation | Tapered roller bearing |
| DE102005058149A1 (en) * | 2005-12-06 | 2007-07-05 | Schaeffler Kg | Tapered roller bearings with curved raceways |
| JP2007210356A (en) * | 2006-02-07 | 2007-08-23 | Ntn Corp | Bearing device for wheel |
| US7281855B2 (en) | 2003-04-25 | 2007-10-16 | Koyo Seiko Co., Ltd. | Tapered roller bearing and final reduction gear |
| DE102006052044A1 (en) * | 2006-11-04 | 2008-05-08 | Ab Skf | Tapered rolling element and tapered roller bearing with the rolling elements |
| KR101383270B1 (en) * | 2012-11-16 | 2014-04-08 | 주식회사 베어링아트 | Taper roller bearing |
| CN109667733A (en) * | 2017-10-13 | 2019-04-23 | 通用电气公司 | Pitch variable bearings and pivoting support bearing for wind turbine |
| CN112253619A (en) * | 2020-11-25 | 2021-01-22 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Large-cone-angle double-row tapered roller bearing for wind power main shaft |
-
1998
- 1998-03-20 JP JP07261198A patent/JP4040160B2/en not_active Expired - Lifetime
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002089553A (en) * | 2000-09-12 | 2002-03-27 | Nsk Ltd | Rolling bearing for continuous casting machine |
| US7281855B2 (en) | 2003-04-25 | 2007-10-16 | Koyo Seiko Co., Ltd. | Tapered roller bearing and final reduction gear |
| WO2007058112A1 (en) * | 2005-11-16 | 2007-05-24 | Ntn Corporation | Tapered roller bearing |
| JP2007139019A (en) * | 2005-11-16 | 2007-06-07 | Ntn Corp | Conical roller bearing |
| EP1956255A4 (en) * | 2005-11-16 | 2012-02-01 | Ntn Toyo Bearing Co Ltd | Tapered roller bearing |
| DE102005058149A1 (en) * | 2005-12-06 | 2007-07-05 | Schaeffler Kg | Tapered roller bearings with curved raceways |
| JP2007210356A (en) * | 2006-02-07 | 2007-08-23 | Ntn Corp | Bearing device for wheel |
| DE102006052044A1 (en) * | 2006-11-04 | 2008-05-08 | Ab Skf | Tapered rolling element and tapered roller bearing with the rolling elements |
| KR101383270B1 (en) * | 2012-11-16 | 2014-04-08 | 주식회사 베어링아트 | Taper roller bearing |
| CN109667733A (en) * | 2017-10-13 | 2019-04-23 | 通用电气公司 | Pitch variable bearings and pivoting support bearing for wind turbine |
| CN112253619A (en) * | 2020-11-25 | 2021-01-22 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Large-cone-angle double-row tapered roller bearing for wind power main shaft |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4040160B2 (en) | 2008-01-30 |
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