JP2003294038A - Tapered roller bearing - Google Patents
Tapered roller bearingInfo
- Publication number
- JP2003294038A JP2003294038A JP2002098757A JP2002098757A JP2003294038A JP 2003294038 A JP2003294038 A JP 2003294038A JP 2002098757 A JP2002098757 A JP 2002098757A JP 2002098757 A JP2002098757 A JP 2002098757A JP 2003294038 A JP2003294038 A JP 2003294038A
- Authority
- JP
- Japan
- Prior art keywords
- tapered roller
- diameter
- annular portion
- roller bearing
- 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.)
- Pending
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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
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、保持器の各ポケッ
トに保持された円すいころが一対の軌道輪間に組み込ま
れている円すいころ軸受に関し、詳しくは保持器の各ポ
ケットの大径側円環部と、各円すいころの大径側端面と
の接触面積を増加させるための円すいころ軸受の保持器
の構造に関する。
【０００２】
【従来の技術】図８に示したように、従来の円すいころ
軸受５０は、環状の保持器６０に形成された複数のポケ
ット６１内に、それぞれ転動自在に保持された複数の円
すいころ５１が一対の軌道輪５２間に組み込まれてい
る。
【０００３】図１０に示したように、保持器６０は、各
ポケット６１内に円すいころ５１を円周方向両側で保持
する柱部６２と、円すいころ５１を軸方向一方側で保持
する大径側円環部６３と、円すいころ５１を軸方向他方
側で保持する小径側円環部６４とを備えている。
【０００４】図１１に示したように、保持器６０のポケ
ット６１の大径側円環部６３は、直線状の平面６３ａに
形成されている。図８に示したように、円すいころ５１
の球状突面である大径側端面５１ａとの接触は、大径側
円環部６３の平面６３ａとの接触となる。図９に示した
ように、両面間の接触形態は、面積の極めて小さい点接
触となり、保持器６０のポケット６１の大径側円環部６
３と、円すいころ５１の大径側端面５１ａとの接触面積
が小さい。
【０００５】
【発明が解決しようとする課題】しかしながら、上述し
た従来の円すいころ軸受５０では、例えば鉄道車両用の
歯車式動力伝達装置に適用した場合、振動及び衝撃が著
しく高い上、高回転で使用されるため、高温度による潤
滑油粘度の低下が起こる。このため、保持器６０のポケ
ット６１の大径側円環部６３の平面６３ａと、各円すい
ころ５１の大径側端面５１ａとの間では、面積の極めて
小さい点接触で、且つ激しい衝突を繰り返しながらの滑
り接触となり、円すいころ５１の大径側端面５１ａが著
しく磨耗してしまうという問題があった。
【０００６】前記現象は、保持器６０の表面硬さの高い
もの、保持器６０のポケット６１の大径側円環部６３と
各円すいころ５１の大径側端面５１ａとの接触面積の小
さいもの、接触面圧の高いもの、又は潤滑状態の良くな
いものに顕著に現れる。このような状態で長期間使用す
ると、円すいころ５１の大径側端面５１ａの形状が変化
してしまい、発熱やカジリを招来し、著しい場合には回
転不能に陥る可能性があった。
【０００７】本発明は、保持器の各ポケットの大径側円
環部と、各円すいころの大径側端面との接触面積を増加
させることができ、当該部位における接触面圧を低下さ
せることができる円すいころ軸受を提供することを目的
としている。
【０００８】
【課題を解決するための手段】本発明の円すいころ軸受
は、環状の保持器に形成された複数のポケット内に転動
自在に保持された複数の円すいころが一対の軌道輪間に
組み込まれている円すいころ軸受において、前記保持器
は、前記ポケット内に前記円すいころを円周方向両側で
保持する柱部と、前記円すいころを軸方向一方側で保持
する大径側円環部と、前記円すいころを軸方向他方側で
保持する小径側円環部とを備え、前記ポケットの前記大
径側円環部は、前記円すいころの大径側端面曲率より大
きい曲率の曲面を有することを特徴とする。
【０００９】前記構成の円すいころ軸受によれば、保持
器の各ポケットの大径側円環部が、各円すいころの大径
側端面曲率より大きい曲率の曲面を有するので、当該部
位の接触は、各ポケットの大径側円環部の曲面と各円す
いころの球状凸面である大径側端面との面接触となる。
これにより、保持器の各ポケットの大径側円環部と、各
円すいころの大径側端面との大きな接触面積が確保され
る。
【００１０】
【発明の実施の形態】以下、本発明の円すいころ軸受の
実施形態を図１乃至図７に基づいて詳細に説明する。図
１は本発明の円すいころ軸受の第１実施形態を示す要部
断面図、図２は、図１におけるポケットの大径側円環部
と円すいころの大径側端面との接触形態を示す要部概略
側面図、図３は図１における保持器を示す斜視図、図４
は図３における保持器の断面図である。
【００１１】図１及び図２に示すように、本実施形態の
円すいころ軸受１０は、保持器２０に保持された複数の
円すいころ１１が一対の内外輪（軌道輪）１２間に組み
込まれている。
【００１２】図１〜図４に示すように、保持器２０は、
鋼板製の保持器本体２１に、複数のポケット２２をプレ
ス打ち抜き加工により形成されており、表面硬化処理が
施されている。各ポケット２２には、各円すいころ１１
を円周方向の両側で保持する柱部２３と、各円すいころ
１１を軸方向一方側（図１中右側）で保持する大径側円
環部２４と、各円すいころ１１を軸方向他方側（図１中
左側）で保持する小径側円環部２５とを備えている。各
ポケット２２の大径側円環部２４は、各円すいころ１１
の大径側端面１１ａの曲率Ｒａより大きい曲率Ｒの凹状
円筒面２４ａ（図４参照）が設けられており、円すいこ
ろ１１の大径側端面１１ａとの大きな接触面積が確保さ
れている。
【００１３】本実施形態の円すいころ軸受の作用を説明
する。図１及び図２に示したように、円すいころ軸受１
０は、保持器２０の各ポケット２２の大径側円環部２４
が、各円すいころ１１の大径側端面１１ａの曲率Ｒａよ
り大きい曲率Ｒの凹状円筒面２４ａを備えている。した
がって、当該部位の接触は、各ポケット２２の大径側円
環部２４の円筒凹面である凹状円筒面２４ａと各円すい
ころ１１の球状凸面である大径側端面１１ａとの面接触
となる。すなわち、２面間の接触形態は、円周方向に長
い楕円接触となる。これにより、保持器２０の各ポケッ
ト２２の大径側円環部２４と、各円すいころ１１の大径
側端面１１ａとの大きな接触面積が確保され、当該接触
部位の滑り接触に伴う磨耗を最少に抑えることができ
る。
【００１４】次に、本発明の円すいころ軸受の第２実施
形態を図５乃至図７に基づいて詳細に説明する。図５は
本発明の円すいころ軸受の第２実施形態を示す要部断面
図、図６は図５におけるポケットの大径側円環部と円す
いころの大径側端面との接触形態を示す要部概略側面
図、図７は図５における保持器を示す断面図である。
【００１５】図５〜図７に示すように、本実施形態の円
すいころ軸受３０は、保持器４０の各ポケット４１の大
径側円環部４２が、各円すいころ１１の大径側端面１１
ａの曲率Ｒａより大きい曲率Ｒの凹状球面４２ａ（図７
参照）を備えている。このＲは、互いに曲率を異ならせ
た凹状球面としても良い。なお、その他の構成について
は、上記第１実施形態と同様であるので、同一構成の部
分については同一符号を付して詳細な説明を省略する。
【００１６】本実施形態の円すいころ軸受の作用を説明
する。図５及び図６に示したように、円すいころ軸受３
０は、保持器４０の各ポケット４１の大径側円環部４２
が、各円すいころ１１の大径側端面１１ａの曲率Ｒａよ
り大きい曲率Ｒの凹状球面を備えている。したがって、
当該部位の接触は、各ポケット４１の大径側円環部４２
の球状凹面である凹状球面４２ａと各円すいころ１１の
球状凸面である大径側端面１１ａとの面接触となる。す
なわち、２面間の接触形態は、円に近い楕円接触とな
る。これにより、保持器４０の各ポケット４１の大径側
円環部４２と、各円すいころ１１の大径側端面１１ａと
の大きな接触面積が確保され、当該接触部位の滑り接触
に伴う磨耗を最少に抑えることができる。
【００１７】上述したように上記各実施形態によれば、
保持器２０，４０の各ポケット２２，４１の大径側円環
部２４，４２が、各円すいころ１１の大径側端面１１ａ
の曲率Ｒａより大きい曲率Ｒの凹状円筒面２４ａ又は凹
状球面４２ａを備えている。したがって、保持器２０，
４０の各ポケット２２，４１の大径側円環部２４，４２
と、各円すいころ１１の大径側端面１１ａとの接触面積
を増加させることができる。よって、当該部位における
接触面圧を低下させることができると共に、滑り発熱量
を減少させることができるので、円すいころ１１の大径
側端面１１ａの磨耗速度を低下させることができ、軸受
１０，３０の信頼性向上を図ることができる。
【００１８】各ポケット２２，４１の大径側円環部２
４，４２と、各円すいころ１１の大径側端面１１ａとの
接触面における発熱量は、面圧、滑り速度、摩擦係数に
影響を受けるが、発熱量を略一定と仮定した場合、面圧
が小さいことにより、滑り速度及び外部荷重を大きくす
ることができる。したがって、滑り速度が大きくなれ
ば、各円すいころ１１の回転速度の向上を図ることがで
きる。また、外部荷重が大きくなれば、より大きな外部
振動や衝撃荷重を受けることができる。
【００１９】更に、各ポケット２２，４１の大径側円環
部２４，４２の磨耗を減少させることができ、各ポケッ
ト２２，４１と円すいころ１１との隙間変化を、長期間
の使用によっても小さく保持することができる。したが
って、各部の強度劣化や疲労の進展を遅らせることがで
き、軸受１０，３０の更なる信頼性向上を図ることがで
きる。
【００２０】
【発明の効果】以上説明したように本発明の円すいころ
軸受によれば、保持器の各ポケットの大径側円環部が、
各円すいころの大径側端面曲率より大きい曲率の曲面を
備えている。したがって、保持器の各ポケットの大径側
円環部と、各円すいころの大径側端面との接触面積を増
加させることができ、当該部位における接触面圧を低下
させることができる。よって、円すいころの大径側端面
の磨耗速度を低下させることができ、軸受の信頼性向上
を図ることができる。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tapered roller bearing in which a tapered roller held in each pocket of a retainer is incorporated between a pair of races. The present invention relates to a tapered roller bearing retainer structure for increasing a contact area between a large-diameter annular portion of each pocket of a retainer and a large-diameter end surface of each tapered roller. As shown in FIG. 8, a conventional tapered roller bearing 50 includes a plurality of pockets 61 formed in an annular retainer 60, each of which is rotatably held by a plurality of pockets 61. Tapered rollers 51 are incorporated between a pair of races 52. As shown in FIG. 10, a retainer 60 has a pillar 62 for holding a tapered roller 51 in each pocket 61 on both sides in the circumferential direction, and a large diameter for holding the tapered roller 51 on one side in the axial direction. A side annular portion 63 and a small-diameter side annular portion 64 that holds the tapered roller 51 on the other side in the axial direction are provided. As shown in FIG. 11, the large-diameter annular portion 63 of the pocket 61 of the retainer 60 is formed on a linear flat surface 63a. As shown in FIG. 8, the tapered rollers 51
The contact with the large-diameter end surface 51a, which is a spherical projection surface, is a contact with the flat surface 63a of the large-diameter annular portion 63. As shown in FIG. 9, the contact form between the two surfaces is a point contact with a very small area, and the large-diameter-side annular portion 6 of the pocket 61 of the retainer 60.
3 has a small contact area with the large-diameter end face 51a of the tapered roller 51. [0005] However, in the above-described conventional tapered roller bearing 50, when applied to, for example, a gear type power transmission device for a railway vehicle, vibration and impact are remarkably high, and high speed rotation is required. Since it is used, lubricating oil viscosity decreases due to high temperature. For this reason, between the flat surface 63a of the large-diameter annular portion 63 of the pocket 61 of the retainer 60 and the large-diameter end surface 51a of each tapered roller 51, repeated point-to-point contact with a very small area and repeated severe collisions are repeated. However, there is a problem that the large-diameter end face 51a of the tapered roller 51 is significantly worn. The above-mentioned phenomenon is caused when the cage 60 has a high surface hardness and the contact area between the large-diameter annular portion 63 of the pocket 61 of the cage 60 and the large-diameter end surface 51a of each tapered roller 51 is small. , Which are remarkably exhibited in those having a high contact surface pressure or poor lubrication. If the tapered roller 51 is used for a long time in such a state, the shape of the large-diameter side end surface 51a of the tapered roller 51 changes, causing heat generation and galling, and in a severe case, it may be impossible to rotate. The present invention can increase the contact area between the large-diameter side annular portion of each pocket of the cage and the large-diameter side end face of each tapered roller, and reduce the contact surface pressure at the relevant portion. It is an object of the present invention to provide a tapered roller bearing that can be used. [0008] A tapered roller bearing according to the present invention comprises a plurality of tapered rollers rotatably held in a plurality of pockets formed in an annular cage. In the tapered roller bearing incorporated in the cage, the retainer includes a pillar portion that holds the tapered roller on both sides in the circumferential direction in the pocket, and a large-diameter-side ring that holds the tapered roller on one side in the axial direction. And a small-diameter-side annular portion that holds the tapered roller on the other side in the axial direction, wherein the large-diameter-side annular portion of the pocket has a curved surface having a curvature larger than the large-diameter-side end surface curvature of the tapered roller. It is characterized by having. According to the tapered roller bearing having the above configuration, the large-diameter annular portion of each pocket of the retainer has a curved surface having a curvature larger than the large-diameter end surface curvature of each tapered roller. Thus, there is surface contact between the curved surface of the large-diameter annular portion of each pocket and the large-diameter end surface which is the spherical convex surface of each tapered roller.
This ensures a large contact area between the large-diameter annular portion of each pocket of the retainer and the large-diameter end surface of each tapered roller. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A tapered roller bearing according to an embodiment of the present invention will be described below in detail with reference to FIGS. FIG. 1 is a sectional view of a main part of a tapered roller bearing according to a first embodiment of the present invention, and FIG. 2 shows a contact form between a large-diameter side annular portion of a pocket and a large-diameter side end face of a tapered roller in FIG. FIG. 3 is a schematic side view of a main part, FIG.
FIG. 4 is a sectional view of the cage in FIG. 3. As shown in FIGS. 1 and 2, a tapered roller bearing 10 of the present embodiment has a plurality of tapered rollers 11 held by a retainer 20 incorporated between a pair of inner and outer rings (track rings) 12. I have. As shown in FIGS. 1 to 4, the retainer 20
A plurality of pockets 22 are formed in a retainer body 21 made of a steel plate by press punching, and a surface hardening process is performed. In each pocket 22, each tapered roller 11
23 that holds the tapered rollers 11 on both sides in the circumferential direction, a large-diameter-side annular portion 24 that holds each tapered roller 11 on one side in the axial direction (right side in FIG. 1), and each other on the other side in the axial direction. (Left side in FIG. 1). The large-diameter annular portion 24 of each pocket 22 is provided with a tapered roller 11.
Is provided with a concave cylindrical surface 24a (see FIG. 4) having a curvature R larger than the curvature Ra of the large-diameter side end face 11a, and a large contact area with the large-diameter side end face 11a of the tapered roller 11 is secured. The operation of the tapered roller bearing of this embodiment will be described. As shown in FIGS. 1 and 2, tapered roller bearing 1
0 is a large-diameter-side annular portion 24 of each pocket 22 of the cage 20.
However, each of the tapered rollers 11 has a concave cylindrical surface 24a having a curvature R larger than the curvature Ra of the large-diameter end surface 11a. Therefore, the contact of the portion is a surface contact between the concave cylindrical surface 24a, which is the cylindrical concave surface of the large-diameter annular portion 24 of each pocket 22, and the large-diameter end surface 11a, which is the spherical convex surface of each tapered roller 11. That is, the contact form between the two surfaces is an elliptical contact that is long in the circumferential direction. Thereby, a large contact area between the large-diameter side annular portion 24 of each pocket 22 of the retainer 20 and the large-diameter side end surface 11a of each tapered roller 11 is ensured, and the abrasion caused by the sliding contact of the contact portion is minimized. Can be suppressed. Next, a tapered roller bearing according to a second embodiment of the present invention will be described in detail with reference to FIGS. FIG. 5 is a cross-sectional view of a main part of a tapered roller bearing according to a second embodiment of the present invention. FIG. 6 is a cross-sectional view showing a contact form between a large-diameter annular portion of a pocket and a large-diameter end face of a tapered roller in FIG. FIG. 7 is a cross-sectional view showing the retainer in FIG. 5. As shown in FIGS. 5 to 7, the tapered roller bearing 30 of the present embodiment is configured such that the large-diameter annular portion 42 of each pocket 41 of the retainer 40 has the large-diameter end surface 11 of each tapered roller 11.
a concave spherical surface 42a having a curvature R larger than the curvature Ra
Reference). This R may be a concave spherical surface having different curvatures from each other. Since other configurations are the same as those of the first embodiment, the same components are denoted by the same reference numerals, and detailed description is omitted. The operation of the tapered roller bearing of this embodiment will be described. As shown in FIGS. 5 and 6, the tapered roller bearing 3
0 is a large-diameter side annular portion 42 of each pocket 41 of the retainer 40.
However, each of the tapered rollers 11 has a concave spherical surface having a curvature R larger than the curvature Ra of the large-diameter end surface 11a. Therefore,
The contact of the portion is performed by the large-diameter annular portion 42 of each pocket 41.
The surface contact between the concave spherical surface 42a, which is a spherical concave surface, and the large-diameter end surface 11a, which is a spherical convex surface of each tapered roller 11, is obtained. That is, the contact form between the two surfaces is an elliptical contact close to a circle. As a result, a large contact area between the large-diameter side annular portion 42 of each pocket 41 of the retainer 40 and the large-diameter side end surface 11a of each tapered roller 11 is ensured, and wear due to sliding contact of the contact portion is minimized. Can be suppressed. As described above, according to the above embodiments,
The large-diameter annular portions 24 and 42 of the pockets 22 and 41 of the retainers 20 and 40 correspond to the large-diameter end surfaces 11 a of the tapered rollers 11.
Is provided with a concave cylindrical surface 24a or a concave spherical surface 42a having a curvature R larger than the curvature Ra. Therefore, the cage 20,
The large-diameter-side annular portions 24, 42 of the respective 40 pockets 22, 41
Thus, the contact area between the tapered roller 11 and the large-diameter end surface 11a can be increased. Therefore, the contact surface pressure at the relevant portion can be reduced, and the amount of heat generated by sliding can be reduced, so that the wear speed of the large-diameter side end surface 11a of the tapered roller 11 can be reduced, and the bearings 10 and 30 can be reduced. Reliability can be improved. Large-diameter-side annular portion 2 of each pocket 22, 41
4, 42 and the amount of heat generated at the contact surface between the tapered roller 11 and the large-diameter end surface 11a are affected by the surface pressure, the sliding speed, and the friction coefficient. Is small, the sliding speed and the external load can be increased. Therefore, if the sliding speed increases, the rotation speed of each tapered roller 11 can be improved. Further, when the external load increases, a larger external vibration or impact load can be received. Furthermore, the wear of the large-diameter annular portions 24, 42 of the pockets 22, 41 can be reduced, and the gap between the pockets 22, 41 and the tapered rollers 11 can be changed even after long-term use. Can be kept small. Therefore, it is possible to delay the deterioration of strength and the progress of fatigue of each part, and it is possible to further improve the reliability of the bearings 10 and 30. As described above, according to the tapered roller bearing of the present invention, the large-diameter annular portion of each pocket of the cage has
Each of the tapered rollers has a curved surface having a curvature larger than that of the large-diameter end surface. Accordingly, the contact area between the large-diameter annular portion of each pocket of the retainer and the large-diameter end surface of each tapered roller can be increased, and the contact surface pressure at the relevant site can be reduced. Therefore, the wear rate of the large-diameter end face of the tapered roller can be reduced, and the reliability of the bearing can be improved.
【図面の簡単な説明】
【図１】本発明の円すいころ軸受の第１実施形態を示す
要部断面図である。
【図２】図１におけるポケットの大径側円環部と円すい
ころの大径側端面との接触形態を示す要部概略側面図で
ある。
【図３】図１における保持器を示す斜視図である。
【図４】図３における保持器の断面図である。
【図５】本発明の円すいころ軸受の第２実施形態を示す
要部断面図である。
【図６】図５におけるポケットの大径側円環部と円すい
ころの大径側端面との接触形態を示す要部概略側面図で
ある。
【図７】図５における保持器を示す断面図である。
【図８】従来の円すいころ軸受を示す要部断面図であ
る。
【図９】図８におけるポケットの大径側円環部と円すい
ころの大径側端面との接触形態を示す要部概略側面図で
ある。
【図１０】図８における保持器を示す斜視図である。
【図１１】図１０における保持器の断面図である。
【符号の説明】
１０ 円すいころ軸受
１１ 円すいころ
１２ 軌道輪（内輪）
２０ 保持器
２１ 保持器本体
２２ ポケット
２３ 柱部
２４ 大径側円環部
２４ａ 凹状円筒面
２５ 小径側円環部
Ｒ 各ポケットの大径側円環部の凹状円筒面の曲
率
Ｒａ 各円すいころの大径側端面の曲率BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view of a main part of a tapered roller bearing according to a first embodiment of the present invention. FIG. 2 is a schematic side view of a main part showing a contact form between a large-diameter annular portion of a pocket and a large-diameter end surface of a tapered roller in FIG. 1; FIG. 3 is a perspective view showing the retainer in FIG. FIG. 4 is a sectional view of the retainer in FIG. FIG. 5 is a sectional view of a main part of a tapered roller bearing according to a second embodiment of the present invention. 6 is a schematic side view of a main part showing a contact form between a large-diameter side annular portion of a pocket and a large-diameter side end surface of a tapered roller in FIG. 5; FIG. 7 is a sectional view showing the retainer in FIG. FIG. 8 is a sectional view of a main part showing a conventional tapered roller bearing. FIG. 9 is a schematic side view of a main part showing a form of contact between the large-diameter annular portion of the pocket and the large-diameter end surface of the tapered roller in FIG. 8; FIG. 10 is a perspective view showing the retainer in FIG. FIG. 11 is a sectional view of the retainer in FIG. [Description of Code] 10 Tapered Roller Bearing 11 Tapered Roller 12 Track Ring (Inner Ring) 20 Cage 21 Cage Body 22 Pocket 23 Column 24 Large Diameter Ring 24a Concave Cylindrical Surface 25 Small Diameter Ring R Each Pocket The curvature Ra of the concave cylindrical surface of the large-diameter annular part of the curvature of the large-diameter end face of each tapered roller
Claims (1)
ト内に転動自在に保持された複数の円すいころが一対の
軌道輪間に組み込まれている円すいころ軸受において、 前記保持器は、前記ポケット内に前記円すいころを円周
方向両側で保持する柱部と、前記円すいころを軸方向一
方側で保持する大径側円環部と、前記円すいころを軸方
向他方側で保持する小径側円環部とを備え、 前記ポケットの前記大径側円環部は、前記円すいころの
大径側端面曲率より大きい曲率の曲面を有することを特
徴とする円すいころ軸受。Claims 1. A tapered roller bearing in which a plurality of tapered rollers rotatably held in a plurality of pockets formed in an annular cage are incorporated between a pair of races. The retainer includes a column portion that holds the tapered rollers on both sides in the circumferential direction in the pocket, a large-diameter side annular portion that holds the tapered rollers on one side in the axial direction, and an axial direction of the tapered rollers. A small-diameter-side annular portion held on the other side, wherein the large-diameter-side annular portion of the pocket has a curved surface having a curvature larger than a large-diameter-side end surface curvature of the tapered roller. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002098757A JP2003294038A (en) | 2002-04-01 | 2002-04-01 | Tapered roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002098757A JP2003294038A (en) | 2002-04-01 | 2002-04-01 | Tapered roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003294038A true JP2003294038A (en) | 2003-10-15 |
Family
ID=29240618
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002098757A Pending JP2003294038A (en) | 2002-04-01 | 2002-04-01 | Tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003294038A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007270949A (en) * | 2006-03-31 | 2007-10-18 | Jtekt Corp | Thrust roller bearing |
| JP2008002538A (en) * | 2006-06-21 | 2008-01-10 | Ntn Corp | Thrust roller bearing |
| US7896558B2 (en) | 2006-06-06 | 2011-03-01 | Ntn Corporation | Thrust roller bearing |
| WO2019172446A1 (en) * | 2018-03-09 | 2019-09-12 | 日本精工株式会社 | Tapered roller bearing |
| JP2021032355A (en) * | 2019-08-26 | 2021-03-01 | 日本精工株式会社 | Tapered roller bearing |
| JP2021032354A (en) * | 2019-08-26 | 2021-03-01 | 日本精工株式会社 | Tapered roller bearing |
-
2002
- 2002-04-01 JP JP2002098757A patent/JP2003294038A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007270949A (en) * | 2006-03-31 | 2007-10-18 | Jtekt Corp | Thrust roller bearing |
| US7896558B2 (en) | 2006-06-06 | 2011-03-01 | Ntn Corporation | Thrust roller bearing |
| JP2008002538A (en) * | 2006-06-21 | 2008-01-10 | Ntn Corp | Thrust roller bearing |
| WO2019172446A1 (en) * | 2018-03-09 | 2019-09-12 | 日本精工株式会社 | Tapered roller bearing |
| CN111868400A (en) * | 2018-03-09 | 2020-10-30 | 日本精工株式会社 | Tapered Roller Bearings |
| JPWO2019172446A1 (en) * | 2018-03-09 | 2021-02-25 | 日本精工株式会社 | Tapered roller bearing |
| US11306774B2 (en) | 2018-03-09 | 2022-04-19 | Nsk Ltd. | Tapered roller bearing |
| CN111868400B (en) * | 2018-03-09 | 2022-06-21 | 日本精工株式会社 | Tapered Roller Bearings |
| JP2021032355A (en) * | 2019-08-26 | 2021-03-01 | 日本精工株式会社 | Tapered roller bearing |
| JP2021032354A (en) * | 2019-08-26 | 2021-03-01 | 日本精工株式会社 | Tapered roller bearing |
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