JP2007192315A - Split roller bearing - Google Patents

Split roller bearing Download PDF

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JP2007192315A
JP2007192315A JP2006011411A JP2006011411A JP2007192315A JP 2007192315 A JP2007192315 A JP 2007192315A JP 2006011411 A JP2006011411 A JP 2006011411A JP 2006011411 A JP2006011411 A JP 2006011411A JP 2007192315 A JP2007192315 A JP 2007192315A
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cage
rollers
roller
roller bearing
split
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Hiroki Mizuno
浩樹 水野
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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
    • F16C33/51—Cages for rollers or needles formed of unconnected members
    • F16C33/513—Cages for rollers or needles formed of unconnected members formed of arcuate segments for carrying one or more rollers
    • F16C33/516—Cages for rollers or needles formed of unconnected members formed of arcuate segments for carrying one or more rollers with two segments, e.g. double-split cages with two semicircular parts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To reduce vibration during the operation generated due to the uneven arrangement of rollers along the circumferential direction of a cage. <P>SOLUTION: The rollers 11a larger in rigidity than the rollers 11b rollingly held by the pockets 24 of the cage 20 are rollingly held by the pockets 23 nearest the circumferential end faces 22 of the split parts 21 of the cage 20. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、軌道輪及び保持器を円周方向に少なくとも二分割されており、例えば自動車用エンジンのクランクシャフトを回転自在に支持するための分割型ころ軸受に関する。   The present invention relates to a split roller bearing for rotatably supporting a crankshaft of an automobile engine, for example, in which a race and a cage are divided at least in the circumferential direction.

従来から自動車用エンジンのクランクシャフトを支持するための軸受としては、組立上の制約から、主として二分割された分割型滑り軸受が使用されていた。しかし、分割型滑り軸受では、高速回転下での摩擦抵抗が大きい。このため、近年、摩擦抵抗の小さいころ軸受を採用することにより、燃費向上等を図る動きがある。   Conventionally, as a bearing for supporting a crankshaft of an automobile engine, a split sliding bearing divided into two has been mainly used due to restrictions on assembly. However, the split type plain bearing has a high frictional resistance under high speed rotation. For this reason, in recent years, there has been a movement to improve fuel efficiency by adopting roller bearings with low frictional resistance.

ここで、ころ軸受の軌道輪及び保持器を二分割して分割型ころ軸受とする場合、軸受運転時の振動が問題となる。すなわち、分割型ころ軸受において、ころの数を多くする方が振動を低減できるので、ころ数を増やすことが望ましい。しかし一方で、ころ数を増やすと、保持器において、ころを転動自在に保持するポケット部間の柱の幅が狭くなる。   Here, when the bearing ring and the cage of the roller bearing are divided into two to form a split roller bearing, vibration during bearing operation becomes a problem. That is, in the split roller bearing, increasing the number of rollers can reduce vibration, so it is desirable to increase the number of rollers. However, on the other hand, when the number of rollers is increased, in the cage, the width of the column between the pocket portions that hold the rollers in a rollable manner is reduced.

このため、図４に示す分割型ころ軸受１００のように、ころ１０１が円周方向に不等配となり、軸受１００運転時、保持器１０２の分割部１０３が負荷圏を通過する際、図５に示すように荷重分布の変動が生じ、変動に起因する振動が発生してしまうという問題があった。
図４は、従来の分割型ころ軸受を示す断面図であり、図５は、図４の分割型ころ軸受の保持器の回転角変化に対する回転軸の変位量変化を示すグラフである。 Therefore, as in the split roller bearing 100 shown in FIG. 4, the rollers 101 are unevenly distributed in the circumferential direction, and when the split portion 103 of the cage 102 passes through the load zone during the operation of the bearing 100, FIG. As shown in FIG. 4, there is a problem that the load distribution fluctuates and vibration due to the fluctuation occurs.
FIG. 4 is a cross-sectional view showing a conventional split roller bearing, and FIG. 5 is a graph showing changes in the amount of displacement of the rotating shaft with respect to changes in the rotation angle of the cage of the split roller bearing of FIG.

そこで、図６及び図７を参照すると、例えば特許文献１で開示されているように、ころ軸受１１０の保持器１１１を形成する板材Ｎにおいて、両端部（分割部両側）の柱部Ｎａの幅Ｐ／２を、それ以外の柱部Ｎｂの幅Ｐより狭くすることにより、ころ１１２の円周方向に沿う不等配を抑制している。
図６は、特許文献１で開示されているころ軸受を適用されたシリンダヘッドのカムシャフト周りを示す要部分解斜視図であり、図７は、図６のころ軸受の保持器を形成する板材を示す平面図である。
特開２００５―１８０４５９号公報（第５〜７頁、第２図及び第７図） 6 and 7, for example, as disclosed in Patent Document 1, in the plate material N forming the cage 111 of the roller bearing 110, the width of the column Na at both ends (both sides of the divided portion). By making P / 2 narrower than the width P of the other pillar portion Nb, uneven distribution along the circumferential direction of the roller 112 is suppressed.
FIG. 6 is an exploded perspective view of the main part showing the periphery of the cam shaft of the cylinder head to which the roller bearing disclosed in Patent Document 1 is applied, and FIG. 7 is a plate material forming the cage of the roller bearing of FIG. FIG.
JP 2005-180459 A (pages 5 to 7, FIGS. 2 and 7)

しかし上述した特許文献１に記載の図６及び図７に示す従来のころ軸受１１０では、保持器１１１における分割部両側の柱部Ｎａの幅Ｐ／２をそれ以外の柱部Ｎｂの幅Ｐより狭くしてもなお、ころ１１２の円周方向に沿う不等配を、軸受性能に悪影響を与えないレベルにまで抑制させることはできないという問題があった。また、保持器１１１の強度を保持する観点から、柱部Ｎａの幅を狭くするにも自ずと限界があった。   However, in the conventional roller bearing 110 shown in FIG. 6 and FIG. 7 described in Patent Document 1 described above, the width P / 2 of the column part Na on both sides of the divided part in the cage 111 is made larger than the width P of the other column part Nb. Even if it is narrowed, there is a problem that the uneven distribution along the circumferential direction of the rollers 112 cannot be suppressed to a level that does not adversely affect the bearing performance. In addition, from the viewpoint of maintaining the strength of the cage 111, there is a limit in reducing the width of the column portion Na.

本発明は、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動を低減させることができる分割型ころ軸受を提供することを目的としている。   An object of the present invention is to provide a split-type roller bearing capable of reducing vibration during bearing operation caused by uneven distribution of rollers along the circumferential direction of a cage.

本発明の上記目的は、下記構成により達成される。
（１） ころの軌道輪及び保持器を円周方向に少なくとも二分割された分割型ころ軸受において、
保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの剛性が、保持器の他のポケット部に転動可能に保持されたころの剛性より大きいことを特徴とする分割型ころ軸受。 The above object of the present invention is achieved by the following configurations.
(1) In the split roller bearing in which the raceway and the cage of the roller are divided at least in the circumferential direction,
The rigidity of the rollers that can be rolled in the pocket portions provided in the vicinity of the respective divided portions of the cage is larger than the rigidity of the rollers that can be rolled in the other pocket portions of the cage. Split roller bearing.

（２） 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころが、保持器の他のポケット部に転動可能に保持されたころより、ヤング率の高い材料からなることを特徴とする前記（１）記載の分割型ころ軸受。   (2) Roller-holding rollers in pocket portions provided in the vicinity of the respective divided portions of the cage are more compliant with the Young's modulus than rollers rollably held in other pocket portions of the cage. The split roller bearing according to (1), which is made of a high material.

（３） 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころのヤング率を最大として、保持器の他のポケット部に転動可能に保持されたころのヤング率が、各分割部から離れるに従って徐々に小さくなることを特徴とする請求項２記載の分割型ころ軸受。   (3) Rollers held in the other pockets of the cage in a rollable manner with the maximum Young's modulus of the rollers held in the pockets provided in the vicinity of the respective divided parts of the cage. The split type roller bearing according to claim 2, wherein the Young's modulus gradually decreases as the distance from each divided portion increases.

（４） 前記ヤング率の高い材料が、セラミックであることを特徴とする前記（２）または（３）記載の分割型ころ軸受。   (4) The split roller bearing according to (2) or (3), wherein the material having a high Young's modulus is ceramic.

（５） 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法が、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法より大きいことを特徴とする前記（１）〜（４）のいずれか記載の分割型ころ軸受。   (5) The longitudinal dimension of the roller held in a rollable manner in a pocket portion provided in the vicinity of each divided portion of the cage is that of the roller held in a rollable manner in another pocket portion of the cage. The split roller bearing according to any one of the above (1) to (4), which is larger than a longitudinal dimension.

（６） 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法が、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法に対して、（保持器のころを円周方向に等配とした時の負荷圏のころ数／保持器の各分割部における円周方向に沿うころの不等配領域の負荷圏のころ数）倍であることを特徴とする前記（５）記載の分割型ころ軸受。   (6) The longitudinal dimension of the roller held in a rollable manner in a pocket portion provided in the vicinity of each divided portion of the cage is the same as that of the roller held in a rollable manner in another pocket portion of the cage. With respect to the longitudinal dimension (the number of rollers in the load area when the rollers of the cage are equally distributed in the circumferential direction / the load area of the uneven distribution region of the rollers along the circumferential direction in each divided portion of the cage Divided roller bearing according to (5) above, characterized in that the number of rollers is twice as many.

（７） 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法を最大として、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法が、各分割部から離れるに従って徐々に小さくなることを特徴とする前記（５）記載の分割型ころ軸受。   (7) Maximum length in the longitudinal direction of the roller held so as to be able to roll in a pocket portion provided in the vicinity of each divided portion of the cage, and is held so as to roll in the other pocket portion of the cage. 2. The split roller bearing according to (5), wherein the longitudinal dimension of the roller gradually decreases as the distance from each split portion increases.

前記（１）記載の分割型ころ軸受では、保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの剛性が、保持器の他のポケット部に転動可能に保持されたころの剛性より大きいので、保持器の各分割部が負荷圏を通過する際における支持する回転軸の変位量が、保持器の各分割部以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。これにより、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動が低減される。   In the split roller bearing described in the above (1), the rigidity of the rollers held so as to be able to roll in pocket portions provided in the vicinity of the respective divided portions of the cage can be rolled in other pocket portions of the cage. Since the rigidity of the rollers held by the roller is larger than the rigidity of the rollers, the displacement amount of the rotating shaft that is supported when each divided portion of the cage passes through the load zone is different from the portion of the cage other than each divided portion that passes through the load zone. The amount of displacement of the rotating shaft at is substantially the same as the amount of displacement. Thereby, the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage is reduced.

前記（２）記載の分割型ころ軸受では、保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころが、保持器の他のポケット部に転動可能に保持されたころより、ヤング率の高い材料からなるので、保持器の各分割部が負荷圏を通過する際における支持する回転軸の変位量が、保持器の各分割部以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。これにより、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動が低減される。   In the split roller bearing described in (2) above, the rollers that are rotatably held in pocket portions provided in the vicinity of the respective divided portions of the cage are held so as to be rollable in other pocket portions of the cage. Since it is made of a material having a higher Young's modulus, the amount of displacement of the rotating shaft that is supported when each divided portion of the cage passes through the load zone is such that the portion other than each divided portion of the cage has a load zone. The amount of displacement of the rotating shaft during passage is suppressed to be substantially equal. Thereby, the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage is reduced.

前記（３）記載の分割型ころ軸受では、保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころのヤング率を最大として、保持器の他のポケット部に転動可能に保持されたころのヤング率が、各分割部から離れるに従って徐々に小さくなるので、保持器の各分割部及び各分割部以外の部位が負荷圏を通過する際における回転軸の変位量が、より均一化される。これにより、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動が低減される。   In the split roller bearing described in the above (3), the Young's modulus of the roller that is slidably held in the pocket portions provided in the vicinity of each split portion of the cage is maximized, and the other pocket portions of the cage are provided. The Young's modulus of the roller held so as to be able to roll gradually decreases as it moves away from each divided part, so that the displacement of the rotating shaft when each part of the cage and parts other than each divided part pass through the load zone The amount is made more uniform. Thereby, the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage is reduced.

前記（４）記載の分割型ころ軸受では、保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころが、セラミックからなるので、保持器の各分割部が負荷圏を通過する際における支持する回転軸の変位量が、保持器の各分割部以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。これにより、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動が低減される。
ヤング率の高い材料であるセラミックの具体例としては、セラミック軸受に多用される窒化珪素（ヤング率：３１０ＧＰａ）、炭化珪素（ヤング率：４２０ＧＰａ）、アルミナ（ヤング率：３５０ＧＰａ）が挙げられる（ヤング率は、「トライボロジー」山本雄二他著、理工学社、ｐ．２３５より引用）。 In the split roller bearing described in (4) above, the rollers that are rollably held in pocket portions provided in the vicinity of the respective divided portions of the cage are made of ceramic, so that each divided portion of the cage is loaded. The amount of displacement of the rotating shaft that is supported when passing through the zone is suppressed to be approximately equal to the amount of displacement of the rotating shaft when a portion other than each divided portion of the cage passes through the load zone. Thereby, the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage is reduced.
Specific examples of ceramics that are materials having a high Young's modulus include silicon nitride (Young's modulus: 310 GPa), silicon carbide (Young's modulus: 420 GPa), and alumina (Young's modulus: 350 GPa) frequently used in ceramic bearings (Young) The rate is quoted from “Tribology” by Yuji Yamamoto et al., Science and Engineering, p.235.

前記（５）記載の分割型ころ軸受では、保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法が、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法より大きいので、保持器の各分割部が負荷圏を通過する際における支持する回転軸の変位量が、保持器の各分割部以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。これにより、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動が低減される。   In the split roller bearing described in the above (5), the longitudinal dimension of the rollers that are rotatably held in the pocket portions provided in the vicinity of the respective divided portions of the cage is transferred to the other pocket portions of the cage. Since it is larger than the longitudinal dimension of the roller held movably, the displacement amount of the rotating shaft that is supported when each divided portion of the cage passes through the load zone, the portion other than each divided portion of the cage is the load zone. The amount of displacement of the rotating shaft when passing through is suppressed to be substantially equal. Thereby, the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage is reduced.

前記（６）記載の分割型ころ軸受では、保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法が、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法より大きく、その倍率が、（保持器のころを円周方向に等配とした時の負荷圏のころ数／保持器の各分割部における円周方向に沿うころの不等配領域の負荷圏のころ数）倍であるので、保持器の各分割部が負荷圏を通過する際における支持する回転軸の変位量が、保持器の各分割部以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。これにより、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動が低減される。   In the split roller bearing described in the above (6), the longitudinal dimension of the rollers held in a rollable manner in pocket portions provided in the vicinity of the respective divided portions of the cage is transferred to the other pocket portions of the cage. It is larger than the longitudinal dimension of the roller held movably, and its magnification is (the number of rollers in the load zone when the rollers of the cage are evenly distributed in the circumferential direction / the circumferential direction of each divided portion of the cage Therefore, the amount of displacement of the rotating shaft to be supported when each divided part of the cage passes through the load area is other than each divided part of the cage. Is suppressed to be approximately equal to the amount of displacement of the rotating shaft when passing through the load zone. Thereby, the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage is reduced.

前記（７）記載の分割型ころ軸受では、保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法を最大として、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法が、各分割部から離れるに従って徐々に小さくなるので、保持器の各分割部及び各分割部以外の部位が負荷圏を通過する際における回転軸の変位量が、より均一化される。これにより、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動が低減される。   In the split roller bearing according to the above (7), the longitudinal dimension of the rollers held in a rollable manner in the pocket portions provided in the vicinity of the respective divided portions of the cage is maximized, and the other pocket portions of the cage are The longitudinal dimension of the roller held so as to be able to roll is gradually reduced as the roller is moved away from each divided portion, so that each divided portion of the cage and a portion other than each divided portion rotate when the portion passes through the load zone. Is more uniform. Thereby, the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage is reduced.

本発明の分割型ころ軸受によれば、保持器の各分割部が負荷圏を通過する際における支持する回転軸の変位量を、保持器の各分割部以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制することができ、保持器の円周方向に沿うころの不等配に起因する軸受運転中の振動を低減させることができる。   According to the split roller bearing of the present invention, the amount of displacement of the rotating shaft that is supported when each divided portion of the cage passes through the load zone, and when the portion other than each divided portion of the cage passes through the load zone. The amount of rotation of the rotating shaft can be suppressed to be substantially the same, and the vibration during the bearing operation due to the uneven distribution of the rollers along the circumferential direction of the cage can be reduced.

本発明により得られる分割型ころ軸受は、自動車用エンジンのクランクシャフト支持用として、低振動、耐高負荷、高耐久性を要求される場合に好適に用いられる。   The split roller bearing obtained by the present invention is suitably used for supporting a crankshaft of an automobile engine when low vibration, high load resistance, and high durability are required.

以下、図示実施形態により、本発明を説明する。
図１は、本発明の第１実施形態である分割型ころ軸受を示す断面図である。 Hereinafter, the present invention will be described with reference to illustrated embodiments.
FIG. 1 is a sectional view showing a split roller bearing according to a first embodiment of the present invention.

図１を参照すると、分割型ころ軸受１０は、円周方向に多数配置されたころ１１ａ，１１ｂと、各ころ１１ａ，１１ｂの軌道面１２ａを内周に有する円環状の外輪（軌道輪）１２と、外輪１２の内周側に配置され、各ころ１１ａ，１１ｂを転動可能に保持する保持器２０とから構成されており、自動車用エンジンのクランクシャフト（図示しない）を支持する軸受として用いられる。   Referring to FIG. 1, a split roller bearing 10 includes a plurality of rollers 11a and 11b arranged in a circumferential direction, and an annular outer ring (orbital ring) 12 having a raceway surface 12a of each of the rollers 11a and 11b on the inner circumference. And a retainer 20 that is disposed on the inner peripheral side of the outer ring 12 and holds the rollers 11a and 11b in a rollable manner, and is used as a bearing that supports a crankshaft (not shown) of an automobile engine. It is done.

分割型ころ軸受１０は、外輪１２及び保持器２０を円周方向に均等に二分割されており、保持器２０の各分割部２１における円周方向端面２２に最も近いポケット部２３に転動可能に保持されたころ１１ａの材料に、保持器２０の他のポケット部２４に転動可能に保持されたころ１１ｂの材料（軸受鋼）より、ヤング率の高いセラミック等の材料を使用される。   The split roller bearing 10 has an outer ring 12 and a cage 20 equally divided into two in the circumferential direction, and can be rolled to a pocket portion 23 closest to the circumferential end surface 22 in each divided portion 21 of the cage 20. For the material of the roller 11a held in this manner, a material such as ceramic having a higher Young's modulus is used than the material of the roller 11b (bearing steel) held so as to be able to roll in the other pocket portion 24 of the cage 20.

ここで、図４に示す従来の分割側ころ軸受１００では、保持器１０２の各分割部１０３が負荷圏を通過する際における支持する回転軸（図示しない）の変位量計算値は、図５に示すように、約１μｍである。   Here, in the conventional divided-side roller bearing 100 shown in FIG. 4, the calculated displacement amount of the rotating shaft (not shown) supported when each divided portion 103 of the cage 102 passes through the load zone is shown in FIG. As shown, it is about 1 μm.

図４に示す従来の分割側ころ軸受１００の保持器１０２の各分割部１０３が負荷圏を通過する際における回転軸の変位量（図５）の計算条件は、下記の通りである。また、図５は、図４に示す状態での保持器１０２の回転角を０°とし、外輪固定、軸回転とした場合の保持器１０２の回転角と回転軸の上下方向変位量との関係を示す。
分割型ころ軸受１００の諸元：
カタログ標準品ＦＷＦ−５０５８２５ベース、ころ径４ｍｍ、ころ丈２１ｍｍ、ころ数２６（２８等配）、P.C.D５４ｍｍ、ラジアル隙間３０μｍ
分割型ころ軸受１００の運転条件：
ラジアル荷重５０００Ｎ、回転数２０００ｒｐｍ Calculation conditions for the amount of displacement of the rotating shaft (FIG. 5) when each divided portion 103 of the cage 102 of the conventional divided roller bearing 100 shown in FIG. 4 passes through the load zone are as follows. FIG. 5 shows the relationship between the rotation angle of the cage 102 and the amount of vertical displacement of the rotation shaft when the rotation angle of the cage 102 in the state shown in FIG. Indicates.
Specifications of split roller bearing 100:
Catalog standard product FWF-505825 base, roller diameter 4mm, roller length 21mm, number of rollers 26 (28 equally), PCD 54mm, radial clearance 30μm
Operating conditions of the split roller bearing 100:
Radial load 5000N, rotation speed 2000rpm

第１実施形態によれば、保持器２０の各分割部２１における円周方向端面２２に最も近いポケット部２３に転動可能に保持されたころ１１ａの材料に、保持器２０の他のポケット部２４に転動可能に保持されたころ１１ｂの材料（軸受鋼）より、ヤング率の高いセラミック等の材料を使用されることにより、保持器２０の各分割部２１が負荷圏を通過する際における支持する回転軸の変位量は、保持器２０の各分割部２１以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。   According to the first embodiment, the other pocket portion of the cage 20 is formed on the material of the roller 11a that is rollably held in the pocket portion 23 closest to the circumferential end surface 22 in each divided portion 21 of the cage 20. By using a material such as a ceramic having a higher Young's modulus than the material (bearing steel) of the roller 11b held so as to be able to roll on 24, each divided portion 21 of the retainer 20 passes through the load zone. The amount of displacement of the rotating shaft to be supported is suppressed to be approximately equal to the amount of displacement of the rotating shaft when a portion other than each divided portion 21 of the cage 20 passes through the load zone.

なお、第１実施形態では、各分割部２１近傍におけるヤング率の高い材料により形成されるころ１１ａは各端面２２について１個であるが、このころ１１ａを各端面２２について複数設定してもよい。また、保持器２０の各分割部２１近傍にそれぞれ設けられたポケット部２３に転動可能に保持されたころ１１ａのヤング率を最大として、保持器２０の他のポケット部２４に転動可能に保持されたころ１１ｂのヤング率が、各分割部２１から離れるに従って徐々に小さくなるように構成してもよい。換言すれば、各分割部２１に近づくに従って徐々にヤング率の高い材料のころ１１ａ，１１ｂとしてもよい。このような構成によれば、回転軸の変位量が、より均一化される。   In the first embodiment, the number of rollers 11a formed of a material having a high Young's modulus in the vicinity of each divided portion 21 is one for each end face 22, but a plurality of rollers 11a may be set for each end face 22. . In addition, the Young's modulus of the roller 11a that is slidably held in the pocket part 23 provided in the vicinity of each divided part 21 of the cage 20 is maximized so that it can roll to the other pocket part 24 of the cage 20. You may comprise so that the Young's modulus of the roller 11b hold | maintained may become small gradually as it leaves | separates from each division part 21. FIG. In other words, the rollers 11a and 11b may be made of a material having a gradually higher Young's modulus as the distance from each divided portion 21 is approached. According to such a configuration, the amount of displacement of the rotating shaft is made more uniform.

図２は、本発明の第２実施形態である分割型ころ軸受の保持器の分割部付近を展開して示す要部平面図である。   FIG. 2 is a plan view of an essential part showing the vicinity of the split portion of the cage of the split roller bearing according to the second embodiment of the present invention.

図２を参照すると、分割型ころ軸受５０は、保持器６０の各分割部６１における円周方向端面６２に最も近いポケット部６３及び２番目に近いポケット部６４に転動可能に保持されたころ６５ａの長手方向寸法を、保持器６０の他のポケット部６６に転動可能に保持されたころ６５ｂの長手方向寸法に対して、（保持器のころを円周方向に等配とした時の負荷圏のころ数／保持器の各分割部における円周方向に沿うころの不等配領域の負荷圏のころ数）倍とされる。なお、負荷圏のころ数は、ころ数、ころ径、軸受隙間、荷重条件により決定される。   Referring to FIG. 2, the split roller bearing 50 is a roller that is rotatably held in a pocket portion 63 that is closest to the circumferential end surface 62 and a pocket portion 64 that is second closest to each split portion 61 of the cage 60. The longitudinal dimension of 65a is the same as the longitudinal dimension of the roller 65b that is slidably held in the other pocket portion 66 of the cage 60 (when the rollers of the cage are equally distributed in the circumferential direction). The number of rollers in the load zone / the number of rollers in the load zone in the uneven distribution region of the rollers along the circumferential direction in each divided portion of the cage. Note that the number of rollers in the load zone is determined by the number of rollers, the roller diameter, the bearing clearance, and the load conditions.

すなわち、図２に示す保持器６０では、各分割部６１にころが存在しないことにより、負荷圏のころ数が各分割部６１以外における５本から４本に減少する場合を想定して、保持器６０の各分割部６１における円周方向端面６２に最も近いポケット部６３及び２番目に近いポケット部６４に転動可能に保持されたころ６５ａの長手方向寸法を、保持器６０の他のポケット部６６に転動可能に保持されたころ６５ｂの長手方向寸法の１．２５倍とされている。これにより、負荷圏のころ数が５本から４本に減少したことに起因する剛性低下がキャンセルされ、保持器６０の各分割部６１が負荷圏を通過する際における保持する回転軸の変位量は、保持器６０の各分割部６１以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。
その他の構成及び作用については、上記第１実施形態と同様である。 In other words, in the cage 60 shown in FIG. 2, assuming that the number of rollers in the load zone decreases from 5 to 4 other than each of the divided portions 61 due to the absence of the rollers in each divided portion 61, The longitudinal dimension of the roller 65a that is slidably held in the pocket portion 63 closest to the circumferential end face 62 and the second closest pocket portion 64 in each divided portion 61 of the cage 60 is defined as another pocket of the cage 60. It is set to 1.25 times the longitudinal direction dimension of the roller 65b held by the part 66 so that rolling is possible. As a result, the reduction in rigidity due to the decrease in the number of rollers in the load zone from 5 to 4 is canceled, and the amount of displacement of the rotating shaft held when each divided portion 61 of the cage 60 passes through the load zone Is suppressed to be approximately equal to the amount of displacement of the rotating shaft when a portion other than each divided portion 61 of the cage 60 passes through the load zone.
Other configurations and operations are the same as those in the first embodiment.

図３は、本発明の第３実施形態である分割型ころ軸受の保持器の分割部付近を展開して示す要部平面図である。   FIG. 3 is a plan view of an essential part showing the vicinity of the split portion of the cage of the split roller bearing according to the third embodiment of the present invention.

図３を参照すると、分割型ころ軸受７０は、保持器８０の各分割部８１における円周方向端面８２に最も近いポケット部８３に転動可能に保持されたころ８４ａの長手方向寸法を最大として、保持器８０の他のポケット部８５に転動可能に保持されたころ８４ｂの長手方向寸法を、各分割部８１から離れるに従って徐々に小さくされる。これにより、保持器８０の各分割部８１が負荷圏を通過する際における保持する回転軸の変位量は、保持器８０の各分割部８１以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制される。
その他の構成及び作用については、上記第１実施形態と同様である。 Referring to FIG. 3, in the split roller bearing 70, the longitudinal dimension of the roller 84 a that is rollably held in the pocket portion 83 closest to the circumferential end surface 82 in each divided portion 81 of the cage 80 is maximized. The longitudinal dimension of the rollers 84b held so as to be able to roll in the other pocket portion 85 of the cage 80 is gradually reduced as the distance from each divided portion 81 increases. Thereby, the displacement amount of the rotating shaft held when each divided portion 81 of the cage 80 passes through the load zone is the amount of displacement of the rotating shaft when the portion other than each divided portion 81 of the cage 80 passes through the load zone. The amount of displacement is suppressed to approximately the same.
Other configurations and operations are the same as those in the first embodiment.

以上のように上記各実施形態によれば、分割型ころ軸受１０，５０，７０の保持器２０，６０，８０の各分割部２１，６１，８１近傍にそれぞれ設けられたポケット部２３，６３，６４，８３に転動可能に保持されたころ１１ａ，６５ａ，８４ａの剛性が、保持器２０，６０，８０の他のポケット部２４，６６，８５に転動可能に保持されたころ１１ｂ，６５ｂ，８４ｂの剛性より大きい。   As described above, according to each of the above-described embodiments, the pocket portions 23, 63, provided in the vicinity of the divided portions 21, 61, 81 of the cages 20, 60, 80 of the split roller bearings 10, 50, 70, respectively. The rollers 11a, 65a, and 84a, which are held rotatably by the rollers 64, 83, have the rigidity of the rollers 11b, 65b held by the other pockets 24, 66, 85 of the cages 20, 60, 80 in a rollable manner. , 84b greater than rigidity.

したがって、保持器２０，６０，８０の各分割部２１，６１，８１が負荷圏を通過する際における支持する回転軸の変位量を、保持器２０，６０，８０の各分割部２１，６１，８１以外の部位が負荷圏を通過する際における回転軸の変位量と略同等に抑制することができる。これにより、保持器２０，６０，８０の円周方向に沿うころ１１ａ，１１ｂ，６５ａ，６５ｂ，８４ａ，８４ｂの不等配に起因する軸受１０，５０，７０運転中の振動を低減させることができる。   Therefore, the amount of displacement of the rotating shaft that is supported when each of the divided portions 21, 61, 81 of the cages 20, 60, 80 passes through the load zone is determined by the amount of displacement of each of the divided portions 21, 61, The amount of displacement of the rotating shaft when a portion other than 81 passes through the load zone can be suppressed to be approximately the same. As a result, it is possible to reduce vibration during operation of the bearings 10, 50, 70 caused by uneven distribution of the rollers 11a, 11b, 65a, 65b, 84a, 84b along the circumferential direction of the cages 20, 60, 80. it can.

本発明の第１実施形態である分割型ころ軸受を示す断面図である。It is sectional drawing which shows the split-type roller bearing which is 1st Embodiment of this invention. 本発明の第２実施形態である分割型ころ軸受の保持器の分割部付近を展開して示す要部平面図である。It is a principal part top view which expand | deploys and shows the division | segmentation part vicinity of the holder | retainer of the split-type roller bearing which is 2nd Embodiment of this invention. 本発明の第３実施形態である分割型ころ軸受の保持器の分割部付近を展開して示す要部平面図である。It is a principal part top view which expand | deploys and shows the division | segmentation part vicinity of the holder | retainer of the split roller bearing which is 3rd Embodiment of this invention. 従来の分割型ころ軸受を示す断面図である。It is sectional drawing which shows the conventional split roller bearing. 図４の分割型ころ軸受の保持器の回転角変化に対する回転軸の変位量変化を示すグラフである。It is a graph which shows the displacement amount change of a rotating shaft with respect to the rotation angle change of the holder | retainer of the split roller bearing of FIG. 特許文献１で開示されているころ軸受を適用されたシリンダヘッドのカムシャフト周りを示す要部分解斜視図である。It is a principal part disassembled perspective view which shows the surroundings of the cam shaft of the cylinder head to which the roller bearing currently disclosed by patent document 1 is applied. 図６のころ軸受の保持器を形成する板材を示す平面図である。It is a top view which shows the board | plate material which forms the holder | retainer of the roller bearing of FIG.

符号の説明Explanation of symbols

１０ 分割型ころ軸受
１１ａ 円周方向端面に最も近いポケット部に転動可能に保持されたころ
１１ｂ 他のポケット部に転動可能に保持されたころ
１２ 軌道輪（外輪）
２０ 保持器
２１ 分割部
２２ 円周方向端面
２３ 円周方向端面近傍のポケット部（円周方向端面に最も近いポケット部）
２４ 他のポケット部 DESCRIPTION OF SYMBOLS 10 Split type roller bearing 11a Roller | roller being held by the pocket part nearest to the circumferential direction end surface 11b Roller | roller being hold | maintained by the other pocket part 12 Rolling ring (outer ring)
20 Cage 21 Dividing part 22 Circumferential end face 23 Pocket part near the circumferential end face (Pocket part closest to the circumferential end face)
24 Other pockets

Claims (7)

ころの軌道輪及び保持器を円周方向に少なくとも二分割された分割型ころ軸受において、
保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの剛性が、保持器の他のポケット部に転動可能に保持されたころの剛性より大きいことを特徴とする分割型ころ軸受。 In the split roller bearing in which the raceway and the cage of the roller are divided into at least two parts in the circumferential direction,
The rigidity of the rollers that can be rolled in the pocket portions provided in the vicinity of the respective divided portions of the cage is larger than the rigidity of the rollers that can be rolled in the other pocket portions of the cage. Split roller bearing. 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころが、保持器の他のポケット部に転動可能に保持されたころより、ヤング率の高い材料からなることを特徴とする請求項１記載の分割型ころ軸受。   Rollers that are slidably held in pockets provided in the vicinity of the respective divided parts of the cage are made of a material having a higher Young's modulus than rollers that are slidably held in other pockets of the cage. The split roller bearing according to claim 1, wherein 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころのヤング率を最大として、保持器の他のポケット部に転動可能に保持されたころのヤング率が、各分割部から離れるに従って徐々に小さくなることを特徴とする請求項２記載の分割型ころ軸受。   The Young's modulus of the roller held movably in the other pocket portion of the cage, with the maximum Young's modulus of the roller held movably in the pocket portion provided in the vicinity of each divided portion of the cage. 3. The split roller bearing according to claim 2, wherein the diameter gradually decreases as the distance from each split portion increases. 前記ヤング率の高い材料が、セラミックであることを特徴とする請求項２または３記載の分割型ころ軸受。   4. The split roller bearing according to claim 2, wherein the material having a high Young's modulus is ceramic. 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法が、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法より大きいことを特徴とする請求項１〜４のいずれか記載の分割型ころ軸受。   The longitudinal dimension of the roller that is rollably held in a pocket portion provided in the vicinity of each divided portion of the cage is the longitudinal dimension of the roller that is rollably held in another pocket portion of the cage. The split roller bearing according to any one of claims 1 to 4, wherein it is larger. 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法が、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法に対して、（保持器のころを円周方向に等配とした時の負荷圏のころ数／保持器の各分割部における円周方向に沿うころの不等配領域の負荷圏のころ数）倍であることを特徴とする請求項５記載の分割型ころ軸受。   The longitudinal dimension of the roller that is rollably held in a pocket portion provided in the vicinity of each divided portion of the cage is the longitudinal dimension of the roller that is rollably held in another pocket portion of the cage. (The number of rollers in the load zone when the rollers of the cage are equally distributed in the circumferential direction / the number of rollers in the load zone in the uneven distribution region of the rollers along the circumferential direction in each divided portion of the cage) 6. The split roller bearing according to claim 5, wherein the divided roller bearing is doubled. 前記保持器の各分割部近傍にそれぞれ設けられたポケット部に転動可能に保持されたころの長手方向寸法を最大として、保持器の他のポケット部に転動可能に保持されたころの長手方向寸法が、各分割部から離れるに従って徐々に小さくなることを特徴とする請求項５記載の分割型ころ軸受。   The length of the roller that can be rolled in the other pocket portion of the cage, with the maximum length in the longitudinal direction of the roller held in the pocket portion provided in the vicinity of each divided portion of the cage as the maximum. 6. The split roller bearing according to claim 5, wherein the directional dimension gradually decreases as the distance from each split portion increases.
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