JP2009174689A - Conical roller bearing - Google Patents

Conical roller bearing Download PDF

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Publication number
JP2009174689A
JP2009174689A JP2008016580A JP2008016580A JP2009174689A JP 2009174689 A JP2009174689 A JP 2009174689A JP 2008016580 A JP2008016580 A JP 2008016580A JP 2008016580 A JP2008016580 A JP 2008016580A JP 2009174689 A JP2009174689 A JP 2009174689A
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Prior art keywords
rolling element
pocket
curved surface
cage
roller bearing
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Japanese (ja)
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Azusa Otani
梓 大谷
Tomoharu Saito
智治 斎藤
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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
    • 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
    • F16C33/49—Cages for rollers or needles comb-shaped
    • F16C33/494—Massive or moulded comb cages
    • F16C33/495—Massive or moulded comb cages formed as one piece cages, i.e. monoblock comb cages
    • F16C33/498—Massive or moulded comb cages formed as one piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • 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
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements

Abstract

<P>PROBLEM TO BE SOLVED: To provide a conical roller bearing capable of eliminating various troubles attributable to accumulation of lubricating oil by suppressing occurrence of the accumulation of the lubricating oil in the bearing. <P>SOLUTION: In the conical roller bearing 21, a rolling element 29 with its outer circumferential surface being formed in a barrel-shaped projecting curved surface is used. Raceway surfaces 24, 27 of inner and outer rings 23, 26 are formed in a recessed curved surface capable of suppressing generation of any edge stress during the axial deviation of the inner and outer rings 23, 26. In a retainer 31, the large diameter side of a pocket 33 is formed in an open-comb shape, and a side surface 35a of a pocket column part 35 is formed in a recessed curved surface corresponding to the barrel-shaped projecting curved surface of the rolling element 29. Further, the opening width at an open end of the pocket 33 is set to be smaller than the outside diameter of an intermediate portion of the rolling element 29. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、内輪外周と外輪内周との間に配置される複数個の転動体相互の周方向の間隔が、内外輪間を周回する保持器により保持される円錐ころ軸受に関する。   The present invention relates to a tapered roller bearing in which a circumferential interval between a plurality of rolling elements arranged between an outer circumference of an inner ring and an inner circumference of an outer ring is held by a cage that circulates between the inner and outer rings.

図５は、従来の円錐ころ軸受の構成を示す要部の断面図である。
円錐ころ軸受１は、内輪３の外周の円錐形軌道面４と外輪６の内周の円錐形軌道面７との間に配置される複数個の転動体９相互の周方向の間隔が、内外輪間を周回する保持器１１により保持されている。 FIG. 5 is a cross-sectional view of a main part showing the configuration of a conventional tapered roller bearing.
The tapered roller bearing 1 has a circumferential interval between a plurality of rolling elements 9 arranged between a conical raceway surface 4 on the outer periphery of the inner ring 3 and a conical raceway surface 7 on the inner periphery of the outer ring 6. It is held by a cage 11 that circulates between the wheels.

一般に、保持器１１としては、図６に示すように、転動体９を収容するポケット１３を、周方向に一定間隔に設けたものである。各ポケット１３は、内外輪間を周回する円環状の一対のリム１４，１５と、これらのリム間に橋渡しされる複数本のポケット柱部１６とによって、転動体９の周囲を囲う窓枠形に形成されている（例えば、特許文献１参照）。   Generally, as the retainer 11, as shown in FIG. 6, pockets 13 for accommodating rolling elements 9 are provided at regular intervals in the circumferential direction. Each pocket 13 has a window frame shape surrounding the periphery of the rolling element 9 by a pair of annular rims 14 and 15 that circulate between the inner and outer rings and a plurality of pocket pillars 16 bridged between the rims. (For example, refer to Patent Document 1).

特開２００５−６９４２１号公報JP 2005-69421 A

ところで、円錐ころ軸受は、自動車の最終減速装置部分などに使用される場合も多い。このような場合では、装置内の潤滑油が、軸受内部の潤滑にも利用されることが少なくない。そして、軸受内への潤滑油供給量が必要以上に多くなる場合も少なくない。
前述の円錐ころ軸受１の場合、装置内の潤滑油は、例えば、内輪３の小鍔３ａ側から軸受内部に流入して、大鍔３ｂ側から流出するが、図６に示した構造の保持器１１の場合は、大鍔３ｂ側に位置しているリム１４が、軸受内の潤滑油の流出の妨げとなり、軸受内に滞留する潤滑油の撹拌抵抗が軸受の回転抵抗を増大させる要因となったり、軸受内に滞留する潤滑油が軸受内の撹拌により許容温度以上に昇温したりして、潤滑油の早期劣化を招く虞があった。 By the way, the tapered roller bearing is often used in a final reduction gear portion of an automobile. In such a case, the lubricating oil in the apparatus is often used for lubricating the inside of the bearing. In many cases, the amount of lubricating oil supplied into the bearing becomes larger than necessary.
In the case of the tapered roller bearing 1 described above, for example, the lubricating oil in the apparatus flows into the bearing from the small collar 3a side of the inner ring 3 and flows out from the large collar 3b side, but the structure shown in FIG. 6 is maintained. In the case of the vessel 11, the rim 14 located on the side of the large cage 3 b prevents the lubricating oil in the bearing from flowing out, and the stirring resistance of the lubricating oil staying in the bearing increases the rotational resistance of the bearing. Or the lubricating oil staying in the bearing may be heated to an allowable temperature or higher by stirring in the bearing, leading to early deterioration of the lubricating oil.

そこで、このような不都合を解消するため、大鍔３ｂ側に位置しているリム１４を切除し軸受内の潤滑油の流れを良くした櫛形の保持器の採用も検討された。しかし、一般の円錐ころ軸受の場合、保持器１１のポケット１３は、転動体９のテーパ形状に合わせて、大鍔３ｂ側に向かってポケット幅が徐々に広がる末広がりの形状をしているため、リム１４を切除すると、ポケット１３と転動体９との引っ掛かりがなくなり、保持器１１が小鍔３ａ側に抜ける虞があった。   Therefore, in order to eliminate such inconvenience, the use of a comb-shaped cage in which the rim 14 located on the side of the large ridge 3b is cut off to improve the flow of lubricating oil in the bearing has been studied. However, in the case of a general tapered roller bearing, the pocket 13 of the cage 11 has a divergent shape in which the pocket width gradually increases toward the side of the large flange 3b in accordance with the taper shape of the rolling element 9. When the rim 14 is excised, there is no possibility that the pocket 13 and the rolling element 9 are caught, and the cage 11 may be pulled out to the side of the gavel 3a.

そこで、本発明の目的は上記課題を解消することに係り、軸受内への潤滑油供給が多い環境で利用される場合でも、軸受内での潤滑油の滞留の発生を抑止して軸受内での潤滑油の滞留に起因していた各種の不都合の発生を解消することができ、更に、保持器の抜け落ちも防止することができる円錐ころ軸受を提供することである。   Accordingly, an object of the present invention is to solve the above-mentioned problems, and even when used in an environment where there is a large amount of lubricating oil supplied to the bearing, the occurrence of the retention of lubricating oil in the bearing is suppressed and It is an object of the present invention to provide a tapered roller bearing capable of eliminating various problems caused by the retention of the lubricating oil and preventing the cage from coming off.

上記目的は下記構成により達成される。
（１）内輪外周の円錐形軌道面と外輪内周の円錐形軌道面との間に配置される複数個の転動体相互の周方向の間隔が、内外輪間を周回する保持器により保持される円錐ころ軸受において、
前記転動体として、軌道面に転動自在に接触する外周面が樽形の凸曲面に形成されたものが使用されると共に、内外輪の各軌道面は、内外輪の軸線ずれの際に前記転動体端部の接触によるエッジ応力の発生を抑止できる凹状曲面に形成され、
前記保持器は、前記転動体を収容するポケットの大径側を開放した櫛形で、且つ、前記転動体の外周面に対向するポケット柱部の側面が、前記転動体の樽形の凸曲面に相応する凹曲面に形成され、更に、ポケット開放端における開口幅が前記転動体の中間部外径よりも小さく設定されていることを特徴とする円錐ころ軸受。 The above object is achieved by the following configuration.
(1) A circumferential interval between a plurality of rolling elements arranged between the conical raceway surface on the outer periphery of the inner ring and the conical raceway surface on the inner periphery of the outer ring is held by a cage that circulates between the inner and outer rings. Tapered roller bearings
As the rolling element, one having an outer peripheral surface that is slidably in contact with the raceway surface formed into a barrel-shaped convex curved surface is used, and each raceway surface of the inner and outer rings has the above-mentioned when the axis of the inner and outer rings is displaced. It is formed in a concave curved surface that can suppress the generation of edge stress due to contact with the rolling element end,
The cage is comb-shaped with the large-diameter side of the pocket accommodating the rolling element open, and the side surface of the pocket column portion facing the outer peripheral surface of the rolling element is a barrel-shaped convex curved surface of the rolling element. A tapered roller bearing, wherein the tapered roller bearing is formed in a corresponding concave curved surface, and the opening width at the pocket open end is set smaller than the outer diameter of the intermediate portion of the rolling element.

（２）上記（１）において、前記保持器が樹脂の射出成形により形成されたことを特徴とする円錐ころ軸受。   (2) The tapered roller bearing according to (1), wherein the retainer is formed by resin injection molding.

上記（１）に記載の円錐ころ軸受では、保持器の構造を櫛形にしたため、軸受内部の潤滑油の内輪大鍔側への流出が保持器によって妨げられることがない。
また、潤滑油供給が多い環境で利用される場合でも、軸受内部に流入した潤滑油を速やかに大鍔側から軸受外に流出させて、軸受内での潤滑油の滞留の発生を抑止することができる。従って、滞留している潤滑油の撹拌抵抗による軸受の回転抵抗の増大や、潤滑油の撹拌による過昇温がまねく潤滑油の早期劣化等といった、潤滑油の滞留に起因していた各種の不都合の発生を解消することができる。
そして、転動体を樽形とすると共に、櫛形の保持器のポケット柱部の側面を転動体の樽形の凸曲面に相応する凹曲面に形成し、且つ、保持器のポケット開放端における開口幅を転動体の中間部外径よりも小さく設定しているため、保持器に抜け方向の力が作用しても、ポケット柱部のポケット開放端側の端部が転動体の中間部に引っ掛かるため、保持器の抜け落ちを防止できて、安定した軸受性能を発揮できる。 In the tapered roller bearing described in the above (1), the cage structure is comb-shaped, and therefore, the cage does not prevent the lubricating oil inside the bearing from flowing to the inner ring large collar side.
In addition, even when used in an environment where there is a large amount of lubricating oil supply, the lubricating oil that has flowed into the bearing is quickly drained out of the bearing from the side of the bush to prevent the accumulation of lubricating oil in the bearing. Can do. Therefore, various inconveniences caused by the retention of the lubricating oil, such as an increase in the rotational resistance of the bearing due to the stirring resistance of the remaining lubricating oil and the early deterioration of the lubricating oil resulting in excessive temperature rise due to the stirring of the lubricating oil. Can be eliminated.
The rolling element has a barrel shape, and the side surface of the pocket column portion of the comb-shaped cage is formed into a concave curved surface corresponding to the barrel-shaped convex curved surface of the rolling body, and the opening width at the pocket open end of the cage Is set to be smaller than the outer diameter of the intermediate part of the rolling element, so even if a force in the pulling direction acts on the cage, the end of the pocket column part on the pocket open end side is caught by the intermediate part of the rolling element The cage can be prevented from falling off, and stable bearing performance can be exhibited.

上記（２）に記載の円錐ころ軸受では、保持器が樹脂の一体成形品であるため、ポケット柱部の側面を樽形の転動体に相応した凹曲面とするなど、保持器に曲面加工部分が多くても、保持器を高精度に量産することができる。   In the tapered roller bearing described in the above (2), since the cage is an integrally molded product of resin, the side surface of the pocket column portion is a concave curved surface corresponding to the barrel-shaped rolling element. Even if there are many, the cage can be mass-produced with high accuracy.

以下、本発明に係る円錐ころ軸受の好適な実施の形態について、図面を参照して詳細に説明する。
図１は本発明に係る円錐ころ軸受の一実施の形態における保持器のポケット柱部を縦断する縦断面図、図２は図１に示した円錐ころ軸受における保持器のポケットを縦断する縦断面図、図３は図１に示した保持器の斜視図、図４は図３に示した保持器の要部拡大図である。 Hereinafter, preferred embodiments of a tapered roller bearing according to the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view longitudinally cutting a pocket column portion of a cage in an embodiment of a tapered roller bearing according to the present invention, and FIG. 2 is a longitudinal sectional view longitudinally cutting a pocket of the cage in the tapered roller bearing shown in FIG. 3 is a perspective view of the cage shown in FIG. 1, and FIG. 4 is an enlarged view of a main part of the cage shown in FIG.

この一実施の形態の円錐ころ軸受２１は、内輪２３の外周の円錐形軌道面２４と外輪２６の内周の円錐形軌道面２７との間に配置される複数個の転動体２９相互の周方向の間隔が、内外輪２３，２６間を周回する保持器３１により保持されている。   The tapered roller bearing 21 according to this embodiment includes a plurality of rolling elements 29 arranged between a conical raceway surface 24 on the outer periphery of the inner ring 23 and a conical raceway surface 27 on the inner periphery of the outer ring 26. The interval in the direction is held by a cage 31 that circulates between the inner and outer rings 23 and 26.

本実施の形態の場合、転動体２９としては、軌道面に転動自在に接触する外周面が、自動調心軸受に採用されているころのように、樽形の凸曲面に形成されたものが使用されている。   In the case of the present embodiment, as the rolling element 29, the outer peripheral surface which is in rolling contact with the raceway surface is formed into a barrel-shaped convex curved surface like a roller employed in a self-aligning bearing. Is used.

また、内外輪２３，２６の各軌道面２４，２７は、厳密には円錐型ではなく、内外輪２３，２６の軸線ずれの際に転動体２９の端部の局部的な接触によるエッジ応力の発生を抑止できる凹状曲面に形成されている。なお、この凹状曲面は、特開２０００−７４０７５号公報に開示されているように、中央部の曲率と両端部との曲率を違えて、エッジ応力の発生の抑止に優れた複合曲面に形成することが望ましい。   In addition, the raceway surfaces 24 and 27 of the inner and outer rings 23 and 26 are not strictly conical, and edge stress due to local contact of the end portions of the rolling elements 29 when the inner and outer rings 23 and 26 are misaligned. It is formed in the concave curved surface which can suppress generation | occurrence | production. The concave curved surface is formed into a complex curved surface excellent in suppressing the occurrence of edge stress by differentiating the curvature at the center and the curvature at both ends, as disclosed in JP-A-2000-74075. It is desirable.

本実施の形態における保持器３１は、図３に示すように、転動体２９を収容するポケット３３を周方向に一定間隔に設けたものであるが、ポケット３３を区画する複数本のポケット柱部３５相互を連結する円環状のリム３７は小径側にのみ設けられていて、転動体２９を収容するポケット３３の大径側を開放した櫛形構造になっている。   As shown in FIG. 3, the retainer 31 in the present embodiment is provided with pockets 33 for accommodating the rolling elements 29 at regular intervals in the circumferential direction, but a plurality of pocket pillars that divide the pockets 33. The annular rim 37 that connects the 35 is provided only on the small-diameter side, and has a comb-like structure in which the large-diameter side of the pocket 33 that accommodates the rolling elements 29 is opened.

また、本実施の形態の保持器３１は、図４に示すように、転動体２９の外周面に対向するポケット柱部３５の側面３５ａが、転動体２９の樽形の凸曲面に相応する逆樽形の凹曲面に形成され、更に、ポケット３３の開放端における開口幅ｗ１が転動体２９の中間部外径Ｄ（図２参照）よりも小さく設定されている。
なお、転動体２９の中間部外径Ｄとは、転動体２９の最大外径を意味するものではなく、転動体２９の端部から徐々に拡径する樽形凸曲線の中間部の外径を意味している。 Further, in the cage 31 of the present embodiment, as shown in FIG. 4, the side surface 35 a of the pocket column portion 35 facing the outer peripheral surface of the rolling element 29 is reversed corresponding to the barrel-shaped convex curved surface of the rolling element 29. It is formed in a barrel-shaped concave curved surface, and the opening width w1 at the open end of the pocket 33 is set smaller than the intermediate part outer diameter D of the rolling element 29 (see FIG. 2).
In addition, the intermediate part outer diameter D of the rolling element 29 does not mean the maximum outer diameter of the rolling element 29, but the outer diameter of the intermediate part of the barrel-shaped convex curve gradually expanding from the end of the rolling element 29. Means.

また、本実施の形態の保持器３１は、樹脂の射出成形により形成された一体物である。
使用する樹脂は、例えば、４６ナイロンや、６６ナイロンなどのポリアミド系樹脂や、ポリブチレンテレフタレートやポリフェレンサルサイド（ＰＰＳ）や、ポリアミドイミド（ＰＡＩ）や、熱可塑性ポリイミドや、ポリエーテルケトン（ＰＥＥＫ）や、ポリエーテルニトリル（ＰＥＮ）などが好適である。
また、上記の樹脂材料に、１０〜５０ｗｔ％の繊維状充填材（例えば、ガラス繊維や炭素繊維など）を適宜添加することにより、保持器の剛性及び寸法精度を向上させることができる。 Further, the cage 31 of the present embodiment is an integral body formed by resin injection molding.
Examples of resins used include polyamide resins such as 46 nylon and 66 nylon, polybutylene terephthalate, polyferlensalside (PPS), polyamideimide (PAI), thermoplastic polyimide, and polyether ketone (PEEK). Polyether nitrile (PEN) and the like are preferable.
Moreover, the rigidity and dimensional accuracy of a cage | basket can be improved by adding 10-50 wt% fibrous filler (for example, glass fiber, carbon fiber, etc.) suitably to said resin material.

内輪２３上への転動体２９及び保持器３１の組み込みは、次のようにして行う。最初に保持器３１の各ポケット３３に転動体２９を配置し、その後、内輪２３の小鍔２３ａ側から、小鍔２３ａを乗り越えさせるようにして、保持器３１及び転動体２９を内輪２３の外周に組み付ける。   The rolling element 29 and the retainer 31 are assembled on the inner ring 23 as follows. First, the rolling elements 29 are arranged in the respective pockets 33 of the cage 31, and then the cage 31 and the rolling elements 29 are arranged on the outer circumference of the inner ring 23 so as to get over the cage 23 a from the side of the collar 23 a of the inner ring 23. Assemble to.

以上に説明した円錐ころ軸受２１では、自動車の最終減速装置部分などに使用されて、減速装置内の潤滑油が円錐ころ軸受２１に供給されるとき、潤滑油は図１の矢印Ａ，Ｂに示すように内輪２３の小鍔２３ａ側から軸受内部に流入して、大鍔２３ｂ側から流出するが、保持器３１の構造を櫛形にしたため、軸受内部の潤滑油の大鍔２３ｂ側への流出が保持器３１によって妨げられることがなく、潤滑油供給が多い環境で利用される場合でも、軸受内部に流入した潤滑油を速やかに大鍔２３ｂ側から軸受外に流出させて、軸受内での潤滑油の滞留の発生を抑止することができる。   In the tapered roller bearing 21 described above, when used in the final reduction gear portion of an automobile and the lubricating oil in the reduction gear is supplied to the tapered roller bearing 21, the lubricating oil is indicated by arrows A and B in FIG. As shown in the drawing, the inner ring 23 flows into the bearing from the small flange 23a side and flows out from the large collar 23b side. However, since the cage 31 has a comb shape, the lubricating oil inside the bearing flows out to the large collar 23b side. Even when used in an environment where there is a large supply of lubricating oil without being obstructed by the cage 31, the lubricating oil that has flowed into the bearing is quickly allowed to flow out of the bearing from the side of the large bush 23b, Occurrence of retention of lubricating oil can be suppressed.

従って、滞留している潤滑油の撹拌抵抗による軸受の回転抵抗の増大や、潤滑油の撹拌による過昇温がまねく潤滑油の早期劣化等といった、潤滑油の滞留に起因していた各種の不都合の発生を解消することができる。   Therefore, various inconveniences caused by the retention of the lubricating oil, such as an increase in the rotational resistance of the bearing due to the stirring resistance of the remaining lubricating oil and the early deterioration of the lubricating oil resulting in excessive temperature rise due to the stirring of the lubricating oil. Can be eliminated.

そして、転動体２９を樽形とすると共に、櫛形の保持器３１のポケット柱部３５の側面３５ａを転動体２９の樽形の凸曲面に相応する凹曲面に形成し、且つ、保持器３１のポケット３３開放端における開口幅ｗ１を転動体２９の中間部外径Ｄよりも小さく設定しているため、保持器３１に抜け方向の力が作用しても、ポケット柱部３５のポケット開放端側の端部が転動体２９の中間部に引っ掛かるため、保持器３１の抜け落ちを防止することもができ、安定した軸受性能を発揮できる。   The rolling element 29 has a barrel shape, the side surface 35a of the pocket column portion 35 of the comb-shaped cage 31 is formed into a concave curved surface corresponding to the barrel-shaped convex curved surface of the rolling element 29, and the cage 31 Since the opening width w1 at the open end of the pocket 33 is set to be smaller than the outer diameter D of the intermediate portion of the rolling element 29, the pocket open end side of the pocket column portion 35 even if a force in the pulling direction acts on the cage 31. Since the end of the hook is caught by the intermediate portion of the rolling element 29, the retainer 31 can be prevented from falling off, and stable bearing performance can be exhibited.

また、本実施の形態の円錐ころ軸受２１では、保持器３１が樹脂の一体成形品であるため、ポケット柱部３５の側面３５ａを樽形の転動体２９に相応した凹曲面とするなど、保持器３１に曲面加工部分が多くても、保持器３１を高精度に量産することができる。   Further, in the tapered roller bearing 21 of the present embodiment, since the retainer 31 is an integrally molded product of resin, the side surface 35a of the pocket column portion 35 is retained as a concave curved surface corresponding to the barrel-shaped rolling element 29. Even if the machine 31 has many curved surface processed parts, the cage 31 can be mass-produced with high accuracy.

なお、保持器３１は、樹脂の一体成形に限らない。金属製にすることもできる。そして、金属板のプレス加工により形成する場合は、ＳＰＣＣなどの低炭素鋼板や、黄銅板、あるいはステンレス鋼板を利用することができる。
また、金属無垢材の切削加工により形成する場合は、高力黄銅や炭素鋼を利用すると良い。 The cage 31 is not limited to resin integral molding. It can also be made of metal. And when forming by the press work of a metal plate, low carbon steel plates, such as SPCC, a brass plate, or a stainless steel plate can be utilized.
Moreover, when forming by cutting of a solid metal material, it is good to use high-strength brass or carbon steel.

本発明に係る円錐ころ軸受の一実施の形態における保持器のポケット柱部を縦断する縦断面図である。It is a longitudinal cross-sectional view which longitudinally cuts the pocket pillar part of the holder | retainer in one Embodiment of the tapered roller bearing which concerns on this invention. 図１に示した円錐ころ軸受における保持器のポケットを縦断する縦断面図である。It is a longitudinal cross-sectional view which longitudinally cuts the pocket of the retainer in the tapered roller bearing shown in FIG. 図１に示した保持器の斜視図である。It is a perspective view of the holder | retainer shown in FIG. 図３に示した保持器の要部拡大図である。It is a principal part enlarged view of the holder | retainer shown in FIG. 従来の円錐ころ軸受の縦断面図である。It is a longitudinal cross-sectional view of the conventional tapered roller bearing. 図５に示した円錐ころ軸受に使用されている保持器の斜視図である。It is a perspective view of the holder | retainer currently used for the tapered roller bearing shown in FIG.

符号の説明Explanation of symbols

２１ 円錐ころ軸受
２３ 内輪
２３ａ 小鍔
２３ｂ 大鍔
２４ 円錐形軌道面
２６ 外輪
２７ 円錐形軌道面
２９ 転動体
３１ 保持器
３３ ポケット
３５ ポケット柱部
３５ａ 側面
３７ リム
Ｄ 転動体の中間部外径
ｗ１ ポケット開放端の開口幅 21 Conical roller bearing 23 Inner ring 23a Small flange 23b Large flange 24 Conical raceway surface 26 Outer ring 27 Conical raceway surface 29 Rolling element 31 Retainer 33 Pocket 35 Pocket column part 35a Side surface 37 Rim D Middle diameter of rolling element w1 Pocket Open end opening width

Claims (2)

内輪外周の円錐形軌道面と外輪内周の円錐形軌道面との間に配置される複数個の転動体相互の周方向の間隔が、内外輪間を周回する保持器により保持される円錐ころ軸受において、
前記転動体として、軌道面に転動自在に接触する外周面が樽形の凸曲面に形成されたものが使用されると共に、内外輪の各軌道面は、内外輪の軸線ずれの際に前記転動体端部の接触によるエッジ応力の発生を抑止できる凹状曲面に形成され、
前記保持器は、前記転動体を収容するポケットの大径側を開放した櫛形で、且つ、前記転動体の外周面に対向するポケット柱部の側面が、前記転動体の樽形の凸曲面に相応する凹曲面に形成され、更に、ポケット開放端における開口幅が前記転動体の中間部外径よりも小さく設定されていることを特徴とする円錐ころ軸受。 A tapered roller in which a circumferential interval between a plurality of rolling elements arranged between a conical raceway surface on the outer periphery of the inner ring and a conical raceway surface on the inner periphery of the outer ring is held by a cage that circulates between the inner and outer rings. In the bearing
As the rolling element, one having an outer peripheral surface that is slidably in contact with the raceway surface formed into a barrel-shaped convex curved surface is used, and each raceway surface of the inner and outer rings has the above-mentioned when the axis of the inner and outer rings is displaced. It is formed in a concave curved surface that can suppress the generation of edge stress due to contact with the rolling element end,
The cage is comb-shaped with the large-diameter side of the pocket accommodating the rolling element open, and the side surface of the pocket column portion facing the outer peripheral surface of the rolling element is a barrel-shaped convex curved surface of the rolling element. A tapered roller bearing, wherein the tapered roller bearing is formed in a corresponding concave curved surface, and the opening width at the pocket open end is set smaller than the outer diameter of the intermediate portion of the rolling element. 前記保持器が樹脂の射出成形により形成されたことを特徴とする請求項１に記載の円錐ころ軸受。   The tapered roller bearing according to claim 1, wherein the cage is formed by injection molding of resin.
JP2008016580A 2008-01-28 2008-01-28 Conical roller bearing Pending JP2009174689A (en)

Priority Applications (1)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013217474A (en) * 2012-04-11 2013-10-24 Nsk Ltd Cage and tapered roller bearing
KR101383270B1 (en) * 2012-11-16 2014-04-08 주식회사 베어링아트 Taper roller bearing
CN113339404A (en) * 2021-05-26 2021-09-03 河南科技大学 Grease lubrication one-way thrust conical sliding bearing

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013217474A (en) * 2012-04-11 2013-10-24 Nsk Ltd Cage and tapered roller bearing
KR101383270B1 (en) * 2012-11-16 2014-04-08 주식회사 베어링아트 Taper roller bearing
CN113339404A (en) * 2021-05-26 2021-09-03 河南科技大学 Grease lubrication one-way thrust conical sliding bearing

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