JP2017008987A - Conical roller bearing and planetary bearing device - Google Patents

Conical roller bearing and planetary bearing device Download PDF

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Publication number
JP2017008987A
JP2017008987A JP2015122862A JP2015122862A JP2017008987A JP 2017008987 A JP2017008987 A JP 2017008987A JP 2015122862 A JP2015122862 A JP 2015122862A JP 2015122862 A JP2015122862 A JP 2015122862A JP 2017008987 A JP2017008987 A JP 2017008987A
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Japan
Prior art keywords
outer ring
annular portion
tapered roller
planetary
cage
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JP2015122862A
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Japanese (ja)
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将太 若山
Shota Wakayama
将太 若山
貴行 鈴木
Takayuki Suzuki
貴行 鈴木
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2015122862A priority Critical patent/JP2017008987A/en
Priority to PCT/JP2016/067919 priority patent/WO2016204220A1/en
Publication of JP2017008987A publication Critical patent/JP2017008987A/en
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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
    • 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
    • F16C19/38—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 two or more rows 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
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To prevent abnormal abrasion at the column part of a holder, in a conical roller bearing arranged between the planetary rotor of a planetary speed reducer and a carrier.SOLUTION: A holder 140 guided in a radial direction by the inner periphery of an outer ring 110 is employed, and a flange 147 projecting toward the inside of an inner ring 120 is provided at a second annular part 142 on the large-diameter part of the holder 140. Consequently, strong contact between a column part 144 of the holder 140 and a conical roller 130 is prevented by centrifugal force, inflow property of lubricant to the inside of a bearing is improved, the lubricant having flowed in is easily delivered to the column part 144 or guided surfaces 145, 146 of the holder 140, and thereby abnormal wear of the column part 144 can be prevented.SELECTED DRAWING: Figure 1

Description

この発明は、遊星減速機に備わる遊星回転体とキャリヤの軸間に配置される円すいころ軸受、及びその円すいころ軸受を用いた遊星軸受装置に関し、特に、超大型ダンプトラックの駆動系に備わる終減速装置用に好適なものに関する。   The present invention relates to a tapered roller bearing disposed between a planetary rotating body and a carrier shaft provided in a planetary reduction gear, and a planetary bearing device using the tapered roller bearing, and more particularly to a terminal provided in a drive system of a very large dump truck. The present invention relates to a device suitable for a reduction gear.

鉱山で用いられるような超大型ダンプトラックでは、ホイールリムの内側に終減速装置が配置されている。この終減速装置は、一般に、遊星減速機を複数段に組み合わせた構造であり、最終段の遊星減速機からの出力をホイールリムに伝達するようになっている。また、各遊星減速機に備わる遊星回転体や転がり軸受は、終減速装置のハウジング内のオイルバスに蓄えられた潤滑油によって潤滑されるようになっている（例えば、特許文献１）。   In a very large dump truck used in a mine, a final reduction gear is disposed inside a wheel rim. This final reduction gear generally has a structure in which planetary reduction gears are combined in a plurality of stages, and the output from the final stage planetary reduction gears is transmitted to the wheel rim. Moreover, the planetary rotating body and the rolling bearing provided in each planetary reduction gear are lubricated by lubricating oil stored in an oil bath in the housing of the final reduction gear (for example, Patent Document 1).

従来、その遊星減速機に備わる遊星回転体とキャリヤの軸間には、一対の円すいころ軸受が配置されている。遊星回転体は、自転しながら公転し、円すいころ軸受及びキャリヤの軸は、遊星回転体と一体に公転する。終減速装置のハウジング内の下部は、オイルバスになっている。オイルバスの潤滑油は、公転する遊星回転体の内側へ入って円すいころ軸受の内部に流入するようになっている（例えば、特許文献２）。   Conventionally, a pair of tapered roller bearings is disposed between the planetary rotator and the carrier shaft provided in the planetary reduction gear. The planetary rotator revolves while rotating, and the tapered roller bearing and the carrier shaft revolve integrally with the planetary rotator. The lower part in the housing of the final reduction gear is an oil bath. The lubricating oil for the oil bath enters the inside of the revolving planetary rotor and flows into the tapered roller bearing (for example, Patent Document 2).

特開２０１２−２０２４１７号公報JP 2012-202417 A 特開２０１１−１８４０４０号公報JP 2011-184040 A

しかしながら、保持器や軸受内部の潤滑油には、保持器の軸受中心軸周りの回転による遠心力のほかに、円すいころ軸受が遊星回転体と一体に公転することによる遠心力も作用する。遊星回転体の公転による遠心力は、円すいころ軸受に負荷域を生じさせると共に、保持器の変形や偏心、軸受内部の潤滑油の偏りを生じさせる原因となる。   However, in addition to the centrifugal force caused by rotation around the bearing center axis of the cage, centrifugal force caused by the tapered roller bearing revolving integrally with the planetary rotating body also acts on the lubricating oil inside the cage and the bearing. Centrifugal force caused by the revolution of the planetary rotor causes a load region in the tapered roller bearing, and causes deformation and eccentricity of the cage and bias of the lubricating oil inside the bearing.

本願発明者らが現行の超大型ダンプの終減速装置における使用環境を調べたところ、円すいころ軸受の公転直径が５００ｍｍ前後になり、その公転速度が５００ｒｐｍを超え、軸受回転速度が１３００ｒｐｍ程度になり、最大の遠心加速度が約７５Ｇになっていた。このように強い遠心加速度が作用すると、軸受内部の潤滑油が負荷域で希薄になり、負荷域と周方向反対側へ偏る傾向が顕著になる。その潤滑条件の悪い負荷域において、遠心加速度による保持器の変形等により柱部が円すいころに強く押し付けられる場合、柱部に異常摩耗が発生して早期に保持器破壊に至る可能性がある。   The inventors of the present application examined the usage environment in the final reduction device of the current ultra-large dump truck, and the revolution diameter of the tapered roller bearing was about 500 mm, the revolution speed exceeded 500 rpm, and the bearing rotation speed became about 1300 rpm. The maximum centrifugal acceleration was about 75G. When strong centrifugal acceleration acts in this manner, the lubricating oil inside the bearing becomes lean in the load region, and the tendency to deviate toward the opposite side in the circumferential direction from the load region becomes significant. When the column part is strongly pressed against the tapered roller due to deformation of the cage due to centrifugal acceleration or the like in a load region where the lubrication conditions are bad, abnormal wear may occur in the column part and the cage may be destroyed at an early stage.

上記の背景に鑑み、この発明が解決しようとする課題は、遊星減速機の遊星回転体及びキャリヤの軸間に配置される円すいころ軸受において、保持器の柱部の異常摩耗を防止することにある。   In view of the above background, the problem to be solved by the present invention is to prevent abnormal wear of the pillar portion of the cage in the tapered roller bearing disposed between the planetary rotating body of the planetary reduction gear and the shaft of the carrier. is there.

上記の課題を達成するため、この発明は、遊星減速機に備わる遊星回転体及びキャリヤの軸間に配置される円すいころ軸受において、外輪と、内輪と、前記外輪及び前記内輪間に介在する円すいころと、前記外輪の内周によって径方向に案内される保持器と、を備え、前記保持器が、第１環状部と、前記第１環状部に比して大径な外径をもった第２環状部と、前記第１環状部及び前記第２環状部間をポケットに分ける柱部と、を有し、前記第２環状部が、前記内輪側へ突き出た鍔を有する構成を採用したものである。   To achieve the above object, the present invention provides a tapered roller bearing disposed between a planetary rotating body and a carrier shaft provided in a planetary reduction gear, wherein the outer ring, the inner ring, and the cone interposed between the outer ring and the inner ring. A roller and a cage guided in a radial direction by an inner circumference of the outer ring, the cage having a first annular portion and an outer diameter larger than that of the first annular portion. It has a second annular portion, and a pillar portion that divides the first annular portion and the second annular portion into pockets, and the second annular portion has a flange that protrudes toward the inner ring side. Is.

上記構成によれば、保持器が外輪の内周によって径方向に案内されるので、柱部と円すいころ間のすきまを転動体案内方式のように狭く設定する必要がない。また、大径な第２環状部が鍔を有するので、保持器の剛性を向上させることもできる。このため、遠心力の作用によって保持器が変形等した場合でも、柱部と円すいころの強い接触を防ぐことができる。さらに、その鍔が、内輪側へ突き出たものなので、軸受内部に流入した潤滑油を軸受内部で引き上げる役割を果たし、軸受内部への潤滑油流入を促進することも期待できる。さらに、保持器が外輪の内周によって径方向に案内されるようにする場合、保持器の外周及び内周の位置を外輪側へ寄せた配置とし、保持器の内周と内輪との間の隙間を広げることが可能である。このため、潤滑油が保持器の内周と内輪との間を通って軸受内部へ流入し易くすることもできる。保持器の内周と内輪との間に流入した潤滑油は、遠心力の作用により、ポケットの柱部と円すいころ間のすきまを通って外輪側へ向かう。このため、柱部や保持器の被案内面に潤滑油を届き易くすることができる。   According to the above configuration, since the cage is guided in the radial direction by the inner circumference of the outer ring, it is not necessary to set the clearance between the column portion and the tapered roller as narrow as in the rolling element guide system. Moreover, since the large-diameter second annular portion has the flange, the rigidity of the cage can be improved. For this reason, even when the cage is deformed by the action of centrifugal force, it is possible to prevent strong contact between the column portion and the tapered roller. Further, since the flange protrudes toward the inner ring side, it plays a role of pulling up the lubricating oil flowing into the bearing inside the bearing, and can be expected to promote the inflow of lubricating oil into the bearing. Further, when the cage is guided in the radial direction by the inner circumference of the outer ring, the outer circumference of the cage and the position of the inner circumference are arranged close to the outer ring side, and between the inner circumference of the cage and the inner ring. It is possible to widen the gap. For this reason, it is possible to make it easier for the lubricating oil to flow into the bearing through the inner circumference of the cage and the inner ring. The lubricating oil flowing between the inner periphery of the cage and the inner ring travels toward the outer ring through the clearance between the pocket column and the tapered roller by the action of centrifugal force. For this reason, it is possible to make the lubricant easily reach the guided surface of the column part or the cage.

したがって、この発明は、上記構成の採用により、遊星減速機の遊星回転体及びキャリヤの軸間に配置される円すいころ軸受において、遠心力による保持器の柱部と円すいころとの強い接触を防ぎ、軸受内部への潤滑油の流入性を向上させ、その流入した潤滑油を柱部や保持器の被案内面に届き易くしているので、柱部の異常摩耗を防止することができる。   Therefore, according to the present invention, in the tapered roller bearing disposed between the planetary rotating body and the carrier shaft of the planetary reduction gear, the strong contact between the retainer column and the tapered roller due to the centrifugal force is prevented by adopting the above configuration. Since the flowability of the lubricating oil into the bearing is improved and the flowing lubricating oil easily reaches the guided surface of the column portion and the cage, abnormal wear of the column portion can be prevented.

この発明の第１実施形態に係る遊星軸受装置の下部側を示す断面図Sectional drawing which shows the lower part side of the planetary bearing apparatus which concerns on 1st Embodiment of this invention. 図１の遊星軸受装置を用いた遊星減速機を示す断面図Sectional drawing which shows the planetary reduction gear using the planetary bearing apparatus of FIG. 図２のＩＩＩ−ＩＩＩ線の断面図Sectional view taken along line III-III in FIG. （ａ）は図１の外輪間座の正面図、（ｂ）は前記（ａ）のＩＶ−ＩＶ線の断面図(A) is a front view of the outer ring spacer of FIG. 1, (b) is a cross-sectional view taken along line IV-IV of (a). この発明の第２実施形態に係る保持器の第２環状部を示す正面図Front view showing a second annular portion of a cage according to a second embodiment of the present invention. （ａ）はこの発明の第３実施形態に係る保持器の第２環状部の部分正面図、（ｂ）は第３実施形態に係る円すいころ軸受を示す断面図(A) is a partial front view of the 2nd annular part of the cage concerning a 3rd embodiment of this invention, (b) is a sectional view showing a tapered roller bearing concerning a 3rd embodiment. この発明の第４実施形態に係る保持器の部分平面図The fragmentary top view of the holder | retainer which concerns on 4th Embodiment of this invention

以下、この発明の第１実施形態に係る円すいころ軸受及びこれを採用した遊星軸受装置（以下、これらを「第１実施形態」と総称する。）を添付図面に基づいて説明する。図１は、第１実施形態の下部側の断面を示す。図２、図３は、第１実施形態を適用した遊星減速機の断面を示す。   Hereinafter, a tapered roller bearing according to a first embodiment of the present invention and a planetary bearing device employing the tapered roller bearing (hereinafter, collectively referred to as “first embodiment”) will be described with reference to the accompanying drawings. FIG. 1 shows a cross section on the lower side of the first embodiment. 2 and 3 show a cross section of the planetary reduction gear to which the first embodiment is applied.

図２、図３に示すように、この遊星軸受装置は、遊星減速機１０に備わる遊星回転体１１をキャリヤ１２の軸１３間に配置される一対の円すいころ軸受１００によって遊星回転体１１を軸１３に対して回転自在に支持するものであり、一対の円すいころ軸受１００の他にも、内輪間座２００と、間座３００と、外輪間座４００とを備えている。   As shown in FIGS. 2 and 3, the planetary bearing device is configured such that the planetary rotating body 11 provided in the planetary speed reducer 10 is supported by a pair of tapered roller bearings 100 disposed between the shafts 13 of the carrier 12. In addition to the pair of tapered roller bearings 100, the inner ring spacer 200, the spacer 300, and the outer ring spacer 400 are provided.

遊星減速機１０は、超大型ダンプトラックのホイールリムの内側に設けられた終減速装置の第１段目の減速を行うものとなっている。その超大型ダンプトラックは、鉱山用であって積載量３００ｔ以上のものを想定している。   The planetary reduction gear 10 performs the first-stage deceleration of the final reduction gear provided inside the wheel rim of the super large dump truck. The super large dump truck is intended for mines and has a load capacity of 300 t or more.

遊星減速機１０は、図２、図３に示すように、入力軸１４に取り付けた太陽歯車１５と、ハウジング１６に固定された内歯車１７との間に両歯車１５、１７に噛み合う遊星歯車としての遊星回転体１１を複数個配置し、出力軸１８に連結されたキャリヤ１２の軸１３に対して各遊星回転体１１を一対の円すいころ軸受１００で回転自在に支持し、太陽歯車１５と内歯車１７との間で自転しながら公転する遊星回転体１１の公転運動を、キャリヤ１２を介して出力軸１８に出力するものである。遊星減速機１０のハウジング１６内の下部には、潤滑油が蓄えられたオイルバス１９が設けられている。公転する遊星回転体１１及び円すいころ軸受１００は、各々の下部側においてオイルバス１９の潤滑油に浸かり、この際、潤滑油が、円すいころ軸受１００の軸受内部へ流入するようになっている。   As shown in FIGS. 2 and 3, the planetary reduction gear 10 is a planetary gear that meshes with both gears 15 and 17 between a sun gear 15 attached to the input shaft 14 and an internal gear 17 fixed to the housing 16. A plurality of planetary rotating bodies 11 are arranged, and each planetary rotating body 11 is rotatably supported by a pair of tapered roller bearings 100 with respect to the shaft 13 of the carrier 12 connected to the output shaft 18. The revolving motion of the planetary rotator 11 revolving while rotating with the gear 17 is output to the output shaft 18 via the carrier 12. An oil bath 19 in which lubricating oil is stored is provided at a lower portion in the housing 16 of the planetary reduction gear 10. The revolving planetary rotor 11 and the tapered roller bearing 100 are immersed in the lubricating oil of the oil bath 19 on the lower side of each, and the lubricating oil flows into the inside of the tapered roller bearing 100 at this time.

太陽歯車１５周りに公転する円すいころ軸受１００の公転直径は５００ｍｍ程度、その公転速度は５００ｒｐｍ程度、このときの軸受回転速度は１３００ｒｐｍ程度、最大の遠心加速度は７５Ｇ程度を想定している。   The tapered roller bearing 100 revolving around the sun gear 15 is assumed to have a revolution diameter of about 500 mm, a revolution speed of about 500 rpm, a bearing rotational speed of about 1300 rpm, and a maximum centrifugal acceleration of about 75 G.

図１に示すように、円すいころ軸受１００は、外輪１１０と、内輪１２０と、外輪１１０及び内輪１２０間に介在する複数の円すいころ１３０と、これら円すいころ１３０を保持する保持器１４０とを備える。外輪１１０、内輪１２０及び保持器１４０の中心軸は、設計上、一致している。以下、中心軸に沿った方向のことを単に「軸方向」といい、中心軸に直角な方向のことを単に「径方向」といい、中心軸周りの円周方向のことを単に「周方向」という。   As shown in FIG. 1, the tapered roller bearing 100 includes an outer ring 110, an inner ring 120, a plurality of tapered rollers 130 interposed between the outer ring 110 and the inner ring 120, and a cage 140 that holds these tapered rollers 130. . The central axes of the outer ring 110, the inner ring 120, and the retainer 140 are identical in design. Hereinafter, the direction along the central axis is simply referred to as “axial direction”, the direction perpendicular to the central axis is simply referred to as “radial direction”, and the circumferential direction around the central axis is simply referred to as “circumferential direction”. "

外輪１１０は、内周に形成された円すい状の軌道面１１１と、軌道面１１１の小径側の縁から軸方向に延びた円筒状の保持器案内面１１２と、軌道面１１１の大径側の縁から軸方向に延びた円筒状の保持器案内面１１３と、外輪１１０の小径側の側面１１４と、外輪１１０の大径側の側面１１５とを有する。ここで、外輪１１０の大径側とは、外輪幅の中央で交差するラジアル平面を境として内径が大径な方の外輪部分のことをいい、外輪１１０の小径側とは、そのラジアル平面を境として内径が小径な方の外輪部分のことをいう。保持器案内面１１２，１１３と、これに隣接する側面１１４，１１５との間は、面取りになっている。   The outer ring 110 includes a conical raceway surface 111 formed on the inner periphery, a cylindrical cage guide surface 112 extending in the axial direction from an edge on the small diameter side of the raceway surface 111, and a large diameter side of the raceway surface 111. It has a cylindrical cage guide surface 113 extending in the axial direction from the edge, a small-diameter side surface 114 of the outer ring 110, and a large-diameter side surface 115 of the outer ring 110. Here, the large diameter side of the outer ring 110 refers to the outer ring portion having a larger inner diameter with a radial plane intersecting at the center of the outer ring width, and the small diameter side of the outer ring 110 refers to the radial plane. The outer ring portion with the smaller inner diameter as a boundary. The cage guide surfaces 112 and 113 and the side surfaces 114 and 115 adjacent to the cage guide surfaces 112 and 113 are chamfered.

内輪１２０は、外周に形成された円すい状の軌道面１２１と、大つば１２２と、小つば１２３とを有する。大つば１２２は、円すいころ１３０の大端面を案内する。小つば１２３は、円すいころ１３０の内輪１２０からの脱落を防ぐ。   The inner ring 120 has a conical raceway surface 121 formed on the outer periphery, a large brim 122, and a small brim 123. The large brim 122 guides the large end face of the tapered roller 130. The small brim 123 prevents the tapered roller 130 from falling off the inner ring 120.

円すいころ１３０は、軌道面１１１，１２１間に介在し、これらに転がり接触する。   The tapered roller 130 is interposed between the raceway surfaces 111 and 121 and is in rolling contact therewith.

図１、図２に示すように、外輪１１０は、遊星回転体１１の内周に嵌合されており、遊星回転体１１と一体に回転する。内輪１２０は、キャリヤ１２の軸１３に嵌合されており、外輪１１０に対して静止する。   As shown in FIGS. 1 and 2, the outer ring 110 is fitted to the inner periphery of the planetary rotator 11 and rotates integrally with the planetary rotator 11. The inner ring 120 is fitted to the shaft 13 of the carrier 12 and is stationary with respect to the outer ring 110.

図１に示すように、保持器１４０は、第１環状部１４１と、この第１環状部１４１に比して大径な外径をもった第２環状部１４２と、これら両環状部１４１，１４２間をポケット１４３に分ける柱部１４４とを有する。保持器１４０は、各ポケット１４３に収まる円すいころ１３０間の周方向間隔を柱部１４４によって保つようになっている。   As shown in FIG. 1, the retainer 140 includes a first annular portion 141, a second annular portion 142 having an outer diameter larger than that of the first annular portion 141, and both the annular portions 141, 142 has a column portion 144 that divides the space 142 into pockets 143. The retainer 140 is configured to maintain the circumferential interval between the tapered rollers 130 that fit in the pockets 143 by the pillar portions 144.

保持器１４０は、外輪１１０の内周に形成された保持器案内面１１２，１１３によって径方向に案内される。保持器１４０は、外輪１１０の保持器案内面１１２，１１３に周方向にすべり接触（案内接触）し得る被案内面１４５，１４６を有する。被案内面１４５は、第１環状部１４１の外周に形成されている。被案内面１４６は、第２環状部１４２の外周に形成されている。これら被案内面１４５，１４６は、それぞれ対応の保持器案内面１１２，１１３と所定の案内すきまをもって径方向に対面可能な円筒状になっている。保持器１４０の最大偏心量が専ら外輪１１０の内周と保持器１４０との接触によって決まるように、案内すきまと、ポケット１４３のポケットすきまとが設定されている。   The cage 140 is guided in the radial direction by the cage guide surfaces 112 and 113 formed on the inner periphery of the outer ring 110. The cage 140 has guided surfaces 145 and 146 that can make sliding contact (guide contact) in the circumferential direction with the cage guide surfaces 112 and 113 of the outer ring 110. The guided surface 145 is formed on the outer periphery of the first annular portion 141. The guided surface 146 is formed on the outer periphery of the second annular portion 142. These guided surfaces 145 and 146 have a cylindrical shape that can face the corresponding cage guide surfaces 112 and 113 in the radial direction with a predetermined guide clearance. The guide clearance and the pocket clearance of the pocket 143 are set so that the maximum eccentric amount of the cage 140 is determined solely by the contact between the inner circumference of the outer ring 110 and the cage 140.

保持器１４０の案内は、第１環状部１４１と外輪１１０の内周間の接触のみで行ってもよいし、第２環状部１４２と外輪１１０の内周間の接触のみで行ってもよいし、柱部１４４と外輪１１０の内周間の案内接触のみで行ってもよいし、第１環状部１４１、第２環状部１４２及び柱部１４４と外輪１１０の内周間の案内接触で行ってもよい。少なくとも第１環状部１４１及び第２環状部１４２と外輪１１０の内周間の案内接触を行えば、遊星回転体１１の自転・公転運動によって保持器１４０に大きな遠心力が作用した際に、保持器１４０が傾きにくくなる。   The cage 140 may be guided only by contact between the first annular portion 141 and the inner periphery of the outer ring 110, or only by contact between the second annular portion 142 and the inner periphery of the outer ring 110. The guide contact between the pillar portion 144 and the inner periphery of the outer ring 110 may be performed only, or the first annular portion 141, the second annular portion 142 and the guide contact between the pillar portion 144 and the inner periphery of the outer ring 110 may be performed. Also good. If the guide contact between at least the first annular portion 141 and the second annular portion 142 and the inner circumference of the outer ring 110 is made, the cage 140 can be held when a large centrifugal force acts on the cage 140 due to the rotation / revolution of the planetary rotating body 11. The instrument 140 becomes difficult to tilt.

保持器１４０と外輪１１０の内周との案内接触は、外輪１１０の内周よりも周長の短い内輪１２０で保持器を案内する場合に比して、周方向に長く生じる。このため、その保持器案内面１１２，１１３と被案内面１４５，１４６の案内接触箇所での接触圧力は、内輪１２０で保持器を案内する場合に比して抑えられる。さらに、保持器案内面１１２，１１３と被案内面１４５，１４６との間のすべり速度は、共に軸１３周りに回転する外輪１１０と保持器１４０との案内接触になるので、軸１３に対して静止する内輪１２０で保持器を案内する場合に比して小さくなる。その接触圧力とすべり速度の積の値が小さい程、保持器案内面１１２，１１３と被案内面１４５，１４６が摩耗しにくくなる。したがって、内輪１２０で保持器を案内する場合に比して、保持器１４０の被案内面１４５，１４６の摩耗防止を図ることができる。   The guide contact between the cage 140 and the inner circumference of the outer ring 110 is longer in the circumferential direction than when the cage is guided by the inner ring 120 having a shorter circumference than the inner circumference of the outer ring 110. For this reason, the contact pressure at the guide contact portion between the cage guide surfaces 112 and 113 and the guided surfaces 145 and 146 is suppressed as compared with the case where the cage is guided by the inner ring 120. Furthermore, since the sliding speed between the cage guide surfaces 112 and 113 and the guided surfaces 145 and 146 is both guided contact between the outer ring 110 rotating around the shaft 13 and the cage 140, This is smaller than when the cage is guided by the stationary inner ring 120. The smaller the product of the contact pressure and the sliding speed, the harder the cage guide surfaces 112 and 113 and guided surfaces 145 and 146 wear. Therefore, it is possible to prevent wear of the guided surfaces 145 and 146 of the cage 140 as compared with the case where the cage is guided by the inner ring 120.

第２環状部１４２は、内輪１２０側に突き出た鍔１４７と、内周全周に連なった溝１４８とを有する。鍔１４７は、第２環状部の内周全周に亘って径方向に突出しており、遠心力に対する第２環状部１４２の剛性を全周に亘って向上させている。   The second annular portion 142 has a flange 147 protruding toward the inner ring 120 side and a groove 148 that is continuous with the entire inner circumference. The flange 147 protrudes in the radial direction over the entire inner circumference of the second annular portion, and improves the rigidity of the second annular portion 142 against the centrifugal force over the entire circumference.

また、鍔１４７は、第２環状部１４２の端に位置し、溝１４８の軸受外部側の溝壁を兼ねるように形成されている。このため、鍔１４７及び溝１４８は、一体となって全周に亘る窪み状を成している。溝１４８は、柱部１４４との連続部付近の強度を確保するため、ポケット１４３から軸方向に所定間隔を取ったところに配置されている。   The flange 147 is located at the end of the second annular portion 142 and is formed so as to also serve as a groove wall on the bearing outer side of the groove 148. For this reason, the flange 147 and the groove 148 are integrally formed in a hollow shape over the entire circumference. The groove 148 is disposed at a predetermined interval in the axial direction from the pocket 143 in order to ensure the strength in the vicinity of the continuous portion with the column portion 144.

第１環状部１４１、第２環状部１４２及び柱部１４４からなる保持器１４０は、円すいころ１３０の中心軸を含む円すい面よりも外輪１１０側に配置されている。このため、潤滑油は、保持器１４０の内周と内輪１２０との間から円すいころ軸受１００の軸受内部に流入したり、軸受外部に逃げたりし易い。   The cage 140 including the first annular portion 141, the second annular portion 142, and the column portion 144 is disposed on the outer ring 110 side with respect to the conical surface including the central axis of the tapered roller 130. For this reason, the lubricating oil easily flows into the inside of the tapered roller bearing 100 from between the inner periphery of the cage 140 and the inner ring 120 or easily escapes to the outside of the bearing.

図２、図３に示す遊星回転体１１の公転によって円すいころ軸受１００がオイルバス１９を通るとき、軸受内部にオイルバス１９の潤滑油が流入する。保持器１４０の回転に伴い、図１に示すように、内輪１２０側に突き出た鍔１４７は、軸受内部に流入した潤滑油を軸受内部で引き上げ、円すいころ軸受１００の軸受内部への潤滑油流入を促進する。また、鍔１４７及び溝１４８が成している窪み状のところでは、オイルバス１９から出る際、円すいころ軸受１００の軸受内部に流入している潤滑油を掬い上げることができる。   When the tapered roller bearing 100 passes through the oil bath 19 due to the revolution of the planetary rotating body 11 shown in FIGS. 2 and 3, the lubricating oil of the oil bath 19 flows into the bearing. As the cage 140 rotates, as shown in FIG. 1, the flange 147 protruding toward the inner ring 120 pulls up the lubricating oil that has flowed into the bearing, and the lubricating oil flows into the bearing of the tapered roller bearing 100. Promote. In addition, in the recessed portion where the flange 147 and the groove 148 are formed, the lubricating oil flowing into the tapered roller bearing 100 can be scooped up when leaving the oil bath 19.

溝１４８は、鍔１４７の径方向の突出量を抑えつつ、窪み状による潤滑油の保持量を多くするためのものである。溝１４８を省略して柱部１４４の内周面を鍔１４７まで延長した場合でも、潤滑油を掬えるような窪み状を成すことは可能である。   The groove 148 is provided to increase the amount of lubricating oil retained by the depression while suppressing the protruding amount of the flange 147 in the radial direction. Even when the groove 148 is omitted and the inner peripheral surface of the column portion 144 is extended to the flange 147, it is possible to form a recess that can receive the lubricating oil.

保持器１４０の全体は、樹脂により形成されている。樹脂製の保持器１４０は、鋼板等の金属製の保持器に比して、成型表面の摩擦係数が比較的小さくなり、保持器１４０の摩耗防止に対して有利であり、また、保持器１４０の剛性が比較的柔らかくなり、柱部１４４が摩耗した場合でも円すいころ１３０の転動面への攻撃性が小さく、軸受損傷に対して有利となり、さらに保持器１４０が比較的軽量なため、円すいころ１３０の自転・公転運動に起因した遠心力による外輪１１０、内輪１２０への攻撃性が小さくなり、結果的に軸受損傷に対して有利となる。   The entire cage 140 is made of resin. The cage made of resin 140 is advantageous in preventing wear of the cage 140 because the friction coefficient of the molding surface is relatively small compared to a cage made of metal such as a steel plate. The rigidity of the roller is relatively soft, and even when the column part 144 is worn, the aggressiveness to the rolling surface of the tapered roller 130 is small, which is advantageous for bearing damage. Aggressiveness to the outer ring 110 and the inner ring 120 due to the centrifugal force resulting from the rotation / revolution motion of the roller 130 is reduced, which is advantageous for bearing damage.

前述の樹脂としては、例えば、ポリアミド樹脂（ＰＡ）、ポリアセタール（ＰＯＭ）、ポリカーボネート（ＰＣ）、ポリエチレンテレフタレート（ＰＥＴ）、ポリブチレンテレフタレート（ＰＢＴ）、ポリエーテルエーテルケトン（ＰＥＥＫ）、ポリフェニレンスルファイド（ＰＰＳ）、ポリテトラフロロエチレン（ＰＴＦＥ）、ポリスルホン（ＰＳＦ）、ポリエーテルサルフォン（ＰＥＳ）、ポリイミド（ＰＩ）、ポリエーテルイミド（ＰＥＩ）といったものを採用することができる。また、樹脂にガラス繊維（ＧＦ）を混ぜたガラス繊維強化樹脂としてもよく、例えば、ＰＡ４６＋ＧＦ、ＰＡ６６＋ＧＦといったものを採用することができる。   Examples of the resin include polyamide resin (PA), polyacetal (POM), polycarbonate (PC), polyethylene terephthalate (PET), polybutylene terephthalate (PBT), polyetheretherketone (PEEK), and polyphenylene sulfide (PPS). ), Polytetrafluoroethylene (PTFE), polysulfone (PSF), polyethersulfone (PES), polyimide (PI), polyetherimide (PEI), and the like can be used. Moreover, it is good also as glass fiber reinforced resin which mixed glass fiber (GF) with resin, For example, things, such as PA46 + GF and PA66 + GF, are employable.

内輪間座２００は、一対の内輪１２０間の軸方向間隔を保つ部材になっている。内輪間座２００は、遊星回転体１１の公転に伴い、軸１３と一体に公転する。内輪間座２００は、一対の内輪１２０のそれぞれに向かって次第に外径を大きくした外径面２０１を有する。断面Ｖ溝状に形成された外径面２０１の両溝縁は、隣接する内輪１２０の側面外周縁と同径になっている。公転する内輪間座２００の外径面２０１によって公転方向に押された潤滑油は、断面Ｖ溝状の外径面２０１に導かれて内輪１２０の側面外周縁付近まで円滑に流れる。このため、潤滑油は、円すいころ軸受１００の軸受内部へ流入し易くなる。   The inner ring spacer 200 is a member that maintains an axial distance between the pair of inner rings 120. The inner ring spacer 200 revolves integrally with the shaft 13 as the planetary rotator 11 revolves. The inner ring spacer 200 has an outer diameter surface 201 whose outer diameter gradually increases toward each of the pair of inner rings 120. Both groove edges of the outer diameter surface 201 formed in the shape of a V-shaped cross section have the same diameter as the outer peripheral edge of the side surface of the adjacent inner ring 120. The lubricating oil pushed in the revolving direction by the outer diameter surface 201 of the revolving inner ring spacer 200 is guided to the outer diameter surface 201 having a V-shaped cross section and smoothly flows to the vicinity of the outer peripheral edge of the side surface of the inner ring 120. For this reason, the lubricating oil easily flows into the bearing of the tapered roller bearing 100.

間座３００は、外輪１１０の側面１１５に軸方向に当てる部材になっている。間座３００は、外輪１１０及び遊星回転体１１と一体に回転する。外輪１１０に向かって次第に内径を大きくした内径面３０１を有する。内径面３０１は、外輪１１０の側面１１５に連なる内径面取りと同径になっている。回転する間座３００の内径面３０１に接した潤滑油は、強い遠心力の作用により、内径面３０１に導かれて外輪１１０の内径面取り付近まで円滑に流れる。このため、潤滑油は、円すいころ軸受１００の軸受内部へ流入し易くなる。   The spacer 300 is a member that contacts the side surface 115 of the outer ring 110 in the axial direction. The spacer 300 rotates integrally with the outer ring 110 and the planetary rotator 11. An inner diameter surface 301 having an inner diameter gradually increasing toward the outer ring 110 is provided. The inner diameter surface 301 has the same diameter as the inner diameter chamfer connected to the side surface 115 of the outer ring 110. The lubricating oil in contact with the inner diameter surface 301 of the rotating spacer 300 is guided to the inner diameter surface 301 and flows smoothly to the vicinity of the inner diameter chamfer of the outer ring 110 by the action of a strong centrifugal force. For this reason, the lubricating oil easily flows into the bearing of the tapered roller bearing 100.

図１、図４（ａ），（ｂ）に示すように、外輪間座４００は、一対の外輪１１０同士の軸方向間隔を保つ部材になっている。外輪間座４００は、外輪１１０及び遊星回転体１１と一体に回転する。外輪間座４００は、一対の外輪１１０に挟まれた基部４０１と、潤滑油を掻き上げるように基部４０１から突き出た複数の突起部４０２とを有する。突起部４０２は、軸方向に沿った端面を周方向の両側に有し、この端面で潤滑油を掻き上げることができる。突起部４０２は、基部４０１の幅中央上で径方向に突出している。回転する外輪間座４００の突起部４０２によって掻き上げられた潤滑油は、主に基部４０１の内周にかかり、その基部４０１の内周上から外輪１１０の側面１１４側の内径面取り付近まで円滑に流れる。このため、潤滑油は、円すいころ軸受１００の軸受内部へ流入し易くなる。   As shown in FIGS. 1, 4 (a) and 4 (b), the outer ring spacer 400 is a member that maintains the axial interval between the pair of outer rings 110. The outer ring spacer 400 rotates integrally with the outer ring 110 and the planetary rotating body 11. The outer ring spacer 400 includes a base 401 sandwiched between the pair of outer rings 110 and a plurality of protrusions 402 protruding from the base 401 so as to scoop up the lubricating oil. The protrusion 402 has end faces along the axial direction on both sides in the circumferential direction, and the end face can scoop up the lubricating oil. The protruding portion 402 protrudes in the radial direction on the center of the width of the base portion 401. The lubricating oil scooped up by the protruding portion 402 of the rotating outer ring spacer 400 is mainly applied to the inner periphery of the base 401, and smoothly from the inner periphery of the base 401 to the vicinity of the inner diameter chamfer on the side surface 114 side of the outer ring 110. Flowing. For this reason, the lubricating oil easily flows into the bearing of the tapered roller bearing 100.

その基部４０１は、内周に螺旋溝４０３を有する。螺旋溝４０３は、軸方向に向かって周方向に捻じれた螺旋状になっており、外輪間座４００の側面に達している。基部４０１の内周にかかった潤滑油は、螺旋溝４０３に入ると、軸方向の速度成分を与えられる。このため、潤滑油は、より外輪１１０の方へ流れ易くなる。   The base 401 has a spiral groove 403 on the inner periphery. The spiral groove 403 has a spiral shape twisted in the circumferential direction toward the axial direction, and reaches the side surface of the outer ring spacer 400. When the lubricating oil applied to the inner periphery of the base 401 enters the spiral groove 403, an axial velocity component is given. For this reason, the lubricating oil is more likely to flow toward the outer ring 110.

第１実施形態は、上述のようなものであり、保持器１４０が外輪１１０の内周によって径方向に案内されるので、柱部１４４と円すいころ１３０間のすきまを転動体案内方式のように狭く設定する必要がなく、また、大径な第２環状部１４２が鍔１４７を有するので、保持器１４０の剛性が向上させられている。このため、第１実施形態は、遠心力の作用によって保持器１４０が変形等した場合でも、柱部１４４と円すいころ１３０の強い接触を防ぐことができる。内輪１２０側へ突き出た鍔１４７は、軸受内部に流入した潤滑油を円すいころ軸受１００の軸受内部で引き上げる役割を果たし、軸受内部への潤滑油流入を促進する。保持器１４０が外輪１１０側へ寄せた配置になっているので、保持器１４０の内周と内輪１２０との間の隙間が広く、潤滑油が保持器１４０の内周と内輪１２０との間を通って軸受内部へ流入し易い。その流入した潤滑油は、遠心力の作用により、ポケット１４３の柱部１４４と円すいころ１３０間のすきまを通って外輪１１０側へ向かう。このため、柱部１４４や保持器１４０の被案内面１４５，１４６に潤滑油が届き易い。このように、第１実施形態は、遊星減速機１０の遊星回転体１１及びキャリヤ１２の軸１３間に配置される円すいころ軸受１００において、遠心力による保持器１４０の柱部１４４と円すいころ１３０との強い接触を防ぎ、円すいころ軸受１００の軸受内部への潤滑油の流入性を向上させ、その流入した潤滑油を柱部１４４や保持器１４０の被案内面１４５，１４６に届き易くしているので、超大型ダンプトラックの駆動系に備わる終減速装置の第１段目のように強い遠心加速度が作用する使用環境であっても、柱部１４４の異常摩耗を防止することができる。   The first embodiment is as described above, and the cage 140 is guided in the radial direction by the inner circumference of the outer ring 110, so that the clearance between the column portion 144 and the tapered roller 130 is as in the rolling element guide system. It is not necessary to set it narrowly, and since the large-diameter second annular portion 142 has the flange 147, the rigidity of the cage 140 is improved. For this reason, 1st Embodiment can prevent the strong contact of the column part 144 and the tapered roller 130, even when the holder | retainer 140 deform | transforms by the effect | action of a centrifugal force. The flange 147 protruding toward the inner ring 120 plays a role of pulling up the lubricating oil flowing into the bearing inside the tapered roller bearing 100 and promotes the inflow of lubricating oil into the bearing. Since the cage 140 is arranged close to the outer ring 110 side, the clearance between the inner circumference of the cage 140 and the inner ring 120 is wide, and the lubricating oil flows between the inner circumference of the cage 140 and the inner ring 120. Easy to flow into the bearing through. The inflowing lubricating oil passes through the gap between the column portion 144 of the pocket 143 and the tapered roller 130 toward the outer ring 110 by the action of centrifugal force. For this reason, it is easy for the lubricating oil to reach the guided portions 145 and 146 of the column portion 144 and the cage 140. Thus, in the first embodiment, in the tapered roller bearing 100 disposed between the planetary rotating body 11 of the planetary speed reducer 10 and the shaft 13 of the carrier 12, the column portion 144 of the retainer 140 and the tapered roller 130 due to centrifugal force. Is improved, and the flowability of the lubricating oil into the inside of the tapered roller bearing 100 is improved, so that the flowing lubricating oil can easily reach the columns 144 and the guided surfaces 145 and 146 of the cage 140. Therefore, abnormal wear of the column portion 144 can be prevented even in a use environment in which strong centrifugal acceleration acts like the first stage of the final reduction gear provided in the drive system of the super large dump truck.

また、第１実施形態は、第２環状部１４２が内周全周に連なった溝１４８を有し、鍔１４７が溝１４８の溝壁を兼ねるように形成されているので、鍔１４７の径方向の突出量を抑えつつ、円すいころ軸受１００の軸受内部に流入している潤滑油を掬い上げて、軸受内部に保持される潤滑油量を多くすることができる。   In the first embodiment, the second annular portion 142 has a groove 148 connected to the entire inner periphery, and the flange 147 is formed so as to also serve as the groove wall of the groove 148. While suppressing the protrusion amount, the lubricating oil flowing into the bearing of the tapered roller bearing 100 can be scooped up to increase the amount of lubricating oil retained inside the bearing.

また、第１実施形態は、一対の内輪１２０間の軸方向間隔を保つ内輪間座２００を備え、その内輪間座２００が一対の内輪１２０のそれぞれに向かって次第に外径を大きくした外径面２０１を有するので、断面Ｖ溝状の外径面２０１によって潤滑油を各内輪１２０の方へ円滑に流れ易くし、ひいては、円すいころ軸受１００の軸受内部へ流入し易くすることができる。   In addition, the first embodiment includes an inner ring spacer 200 that maintains an axial interval between the pair of inner rings 120, and the inner ring spacer 200 gradually increases in outer diameter toward each of the pair of inner rings 120. Since the outer diameter surface 201 having a V-shaped cross section is provided, the lubricating oil can easily flow smoothly toward the inner rings 120, and can easily flow into the tapered roller bearing 100.

また、第１実施形態は、外輪１１０の側面１１５に軸方向に当てる間座３００を備え、その間座３００が外輪１１０に向かって次第に内径を大きくした内径面３０１を有するので、内径面３０１によって潤滑油を外輪１１０の方へ円滑に流れ易くし、ひいては、円すいころ軸受１００の軸受内部へ流入し易くすることができる。   Further, the first embodiment includes a spacer 300 that is axially applied to the side surface 115 of the outer ring 110, and the spacer 300 has an inner diameter surface 301 that gradually increases in inner diameter toward the outer ring 110. It is possible to facilitate the smooth flow of oil toward the outer ring 110, and to facilitate the flow of oil into the tapered roller bearing 100.

また、第１実施形態は、一対の外輪１１０間の軸方向間隔を保つ外輪間座４００を備え、その外輪間座４００が一対の外輪１１０に挟まれた基部４０１と、潤滑油を掻き上げるように基部４０１から突き出た突起部４０２とを有するので、潤滑油を突起部４０２によって掻き上げ、さらに基部４０１の内周上から外輪１１０の方へ円滑に流れ易くし、ひいては、円すいころ軸受１００の軸受内部へ流入し易くすることができる。   In addition, the first embodiment includes an outer ring spacer 400 that maintains an axial distance between the pair of outer rings 110, and the outer ring spacer 400 scoops up lubricating oil with a base 401 sandwiched between the pair of outer rings 110. Since the protrusion 402 protrudes from the base 401, the lubricating oil is scraped up by the protrusion 402, and further smoothly flows from the inner periphery of the base 401 toward the outer ring 110. As a result, the tapered roller bearing 100 It can be made easy to flow into the bearing.

また、第１実施形態は、その基部４０１が内周に形成された螺旋溝４０３を有するので、基部４０１の内周にかかった潤滑油をより外輪１１０の方へ流れ易くすることができる。   Further, in the first embodiment, since the base portion 401 has the spiral groove 403 formed on the inner periphery, the lubricating oil applied to the inner periphery of the base portion 401 can be more easily flowed toward the outer ring 110.

このように、円すいころ軸受の軸受内部に潤滑油を様々な工夫で流入し易くすると、軸受内部で潤滑油を潤沢にすることができ、摩耗防止だけでなく、軸受内部を潤滑油で冷却し易くもなる。潤滑に寄与した潤滑油は高温になり易く、軸受内部の温度上昇も問題になるような使用環境の場合には、軸受内部の潤滑油を軸受外部へ排出し易くし、軸受内部と外部間での潤滑油の循環を促して温度上昇を抑えることが好ましい。外輪の内周によって保持器が案内される場合、円すいころと軌道面間の転がり接触、外輪と保持器間の案内接触が軸受内部の外輪側で生じ、その軸受内部の外輪側で潤滑油が潤沢になるので、積極的に軸受外部へ排出する余裕がある。その一例としての第２実施形態を図５に基づいて説明する。なお、以下では、第１実施形態との相違点を述べるに留める。   As described above, if the lubricating oil can easily flow into the bearing of the tapered roller bearing by various means, the lubricating oil can be enriched inside the bearing, which not only prevents wear but also cools the inside of the bearing with the lubricating oil. It becomes easy. In a usage environment where the lubricating oil that contributes to lubrication tends to become hot and the temperature rise inside the bearing also becomes a problem, it is easy to discharge the lubricating oil inside the bearing to the outside of the bearing, and between the inside and outside of the bearing. It is preferable to suppress the temperature rise by promoting circulation of the lubricating oil. When the cage is guided by the inner circumference of the outer ring, rolling contact between the tapered roller and the raceway surface, and guide contact between the outer ring and the cage occur on the outer ring side inside the bearing, and the lubricating oil is generated on the outer ring side inside the bearing. Because it becomes abundant, there is room for positive discharge to the outside of the bearing. A second embodiment as an example thereof will be described with reference to FIG. Hereinafter, only differences from the first embodiment will be described.

同図に示すように、第２実施形態では、第２環状部１４２の鍔１４７が周方向に断続的に設けられている。周方向に隣接する鍔１４７間は、軸方向に貫通した油溝１４９になっている。円すいころ軸受に特有のポンプ作用により、軸受内部の潤滑油は、内輪側から外輪側へ、また外輪の小径側から大径側の方へ流れ易い傾向がある。このため、外輪の大径側と同側に位置する第２環状部１４２を横断する油溝１４９があれば、軸受内部の流れ傾向を利用して軸受内部の潤滑油を排出や、軸受内部と外部間での潤滑油の循環を促し、温度上昇を抑えることができる。   As shown in the figure, in the second embodiment, the flange 147 of the second annular portion 142 is provided intermittently in the circumferential direction. An oil groove 149 penetrating in the axial direction is formed between the flanges 147 adjacent in the circumferential direction. Due to the pumping action unique to the tapered roller bearing, the lubricating oil inside the bearing tends to easily flow from the inner ring side to the outer ring side and from the smaller diameter side to the larger diameter side of the outer ring. For this reason, if there is an oil groove 149 that crosses the second annular portion 142 located on the same side as the large diameter side of the outer ring, the lubricating oil inside the bearing can be discharged using the flow tendency inside the bearing, The circulation of the lubricating oil between the outside can be promoted, and the temperature rise can be suppressed.

別例としての第３実施形態を図６（ａ），（ｂ）に基づいて説明する。第３実施形態の保持器１５０は、第１環状部１５１及び第２環状部１５２間をポケット１５３に分ける柱部１５４に対して周方向位置をずらした第２環状部１５２の外周及び鍔１５５にそれぞれ設けられた油溝１５６と、同じくずらした第１環状部１５１の外周及び内周にそれぞれ設けられた油溝１５７とを有する。外周側の油溝１５６は、第２環状部１５２の被案内面１５８を周方向に分断するように凹んでいる。また、外周側の油溝１５７は、第１環状部１５１の被案内面１５９を周方向に分断するように凹んでいる。   A third embodiment as another example will be described with reference to FIGS. The cage 150 according to the third embodiment is formed on the outer periphery of the second annular portion 152 and the flange 155 that are shifted in the circumferential direction with respect to the pillar portion 154 that divides the first annular portion 151 and the second annular portion 152 into pockets 153. Oil grooves 156 provided respectively, and oil grooves 157 provided respectively on the outer periphery and the inner periphery of the first annular portion 151 that are shifted in the same manner. The outer peripheral oil groove 156 is recessed so as to divide the guided surface 158 of the second annular portion 152 in the circumferential direction. Moreover, the oil groove 157 on the outer peripheral side is recessed so as to divide the guided surface 159 of the first annular portion 151 in the circumferential direction.

第３実施形態は、第１環状部１５１及び第２環状部１５２の少なくとも一方が外輪１６０の内周に周方向にすべり接触し得る被案内面１５８，１５９と、被案内面１５８，１５９を周方向に分断するように凹んだ油溝１５６，１５７を有するので、第１環状部、第２環状部との間の案内すきまで潤滑油の流通性を向上させ、案内接触時の油膜切れの防止と、軸受内部及び外部間での潤滑油の循環を両立させることができる。   In the third embodiment, at least one of the first annular portion 151 and the second annular portion 152 is guided around the guided surfaces 158 and 159 that can slide in the circumferential direction on the inner periphery of the outer ring 160 and the guided surfaces 158 and 159. Since it has oil grooves 156 and 157 that are recessed so as to be divided in the direction, it improves the flowability of the lubricating oil up to the guide clearance between the first annular portion and the second annular portion, and prevents oil film breakage at the time of guide contact And the circulation of the lubricating oil between the inside and outside of the bearing can be achieved.

また、第３実施形態は、柱部１５４に対して周方向位置をずらした油溝１５６，１５７を採用しているので、特に、ポケット１５３内を潤滑、冷却した潤滑油を排出し易くすることができる。   In addition, since the third embodiment employs oil grooves 156 and 157 whose positions in the circumferential direction are shifted with respect to the column portion 154, it is particularly easy to discharge the lubricating oil that has been lubricated and cooled in the pocket 153. Can do.

上述のような油溝は、軸方向に沿った直線溝にする必要性はなく、第１環状部又は第２環状部の外径又は内径を規定する面、例えば被案内面を横断するものであればよい。さらに別例としての第４実施形態を図７に示す。第４実施形態の保持器１７０は、第１環状部１７１及び第２環状部１７２間をポケット１７３に分ける柱部１７４のところを除き、第１環状部１７１，第２環状部１７２のそれぞれの外周に、螺旋状の油溝１７７と、被案内面１７５，１７６とを有する。なお、図中では油溝１７７と被案内面１７５，１７６のパターンを見易くするため、油溝１７７の両域を黒塗りしている。油溝１７７は、軸方向に向かって周方向に捻じれた螺旋状になっている。保持器１７０の回転中に潤滑油が油溝１７７に入ると、軸方向の速度成分を与えられる。このため、第４実施形態は、特に、被案内面１７５，１７６を潤滑、冷却した潤滑油を軸受外部へ排出し易くすることができる。なお、第１環状部１７１の内周側、第２環状部１７２の内周側は、螺旋溝を適宜に設けてもよい。   The oil groove as described above does not have to be a linear groove along the axial direction, but crosses a surface that defines the outer diameter or inner diameter of the first annular portion or the second annular portion, for example, a guided surface. I just need it. FIG. 7 shows a fourth embodiment as another example. The retainer 170 according to the fourth embodiment has outer peripheries of the first annular portion 171 and the second annular portion 172 except for the column portion 174 that divides the first annular portion 171 and the second annular portion 172 into pockets 173. In addition, a spiral oil groove 177 and guided surfaces 175 and 176 are provided. In the figure, both areas of the oil groove 177 are painted black to make the pattern of the oil groove 177 and guided surfaces 175 and 176 easier to see. The oil groove 177 has a spiral shape twisted in the circumferential direction toward the axial direction. When the lubricating oil enters the oil groove 177 during the rotation of the cage 170, an axial speed component is given. For this reason, especially 4th Embodiment can make it easy to discharge | emit the lubricating oil which lubricated and cooled the to-be-guided surfaces 175 and 176 to the bearing exterior. In addition, you may provide a spiral groove suitably in the inner peripheral side of the 1st annular part 171 and the inner peripheral side of the 2nd annular part 172. FIG.

今回開示された実施形態はすべての点で例示であって制限的なものではないと考えられるべきである。したがって、本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。   It should be thought that embodiment disclosed this time is an illustration and restrictive at no points. Accordingly, the scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

１０ 遊星減速機
１１ 遊星回転体
１２ キャリヤ
１３ 軸
１００ 円すいころ軸受
１１０，１６０ 外輪
１１２，１１３ 保持器案内面
１２０ 内輪
１３０ 円すいころ
１４０，１５０，１７０ 保持器
１４１，１５１，１７１ 第１環状部
１４２，１５２，１７２ 第２環状部
１４３，１５３，１７３ ポケット
１４４，１５４，１７４ 柱部
１４５，１４６，１５８，１５９，１７８ 被案内面
１４７，１５５ 鍔
２００ 内輪間座
２０１ 外径面
３００ 間座
３０１ 内径面
４００ 外輪間座
４０１ 基部
４０２ 突起部
４０３ 螺旋溝 DESCRIPTION OF SYMBOLS 10 Planetary reduction gear 11 Planetary rotating body 12 Carrier 13 Shaft 100 Tapered roller bearing 110,160 Outer ring 112,113 Cage guide surface 120 Inner ring 130 Tapered roller 140,150,170 Cage 141,151,171 First annular part 142, 152, 172 Second annular portion 143, 153, 173 Pocket 144, 154, 174 Column portion 145, 146, 158, 159, 178 Guided surface 147, 155 鍔 200 Inner ring spacer 201 Outer diameter surface 300 Spacer 301 Inner diameter surface 400 Outer ring spacer 401 Base 402 Projection 403 Spiral groove

Claims (7)

遊星減速機に備わる遊星回転体及びキャリヤの軸間に配置される円すいころ軸受において、
外輪と、
内輪と、
前記外輪及び前記内輪間に介在する円すいころと、
前記外輪の内周によって径方向に案内される保持器と、
を備え、
前記保持器が、第１環状部と、前記第１環状部に比して大径な外径をもった第２環状部と、前記第１環状部及び前記第２環状部間をポケットに分ける柱部と、を有し、
前記第２環状部が、前記内輪側へ突き出た鍔を有することを特徴とする円すいころ軸受。 In the tapered roller bearing disposed between the planetary rotating body and the carrier shaft provided in the planetary reduction gear,
Outer ring,
Inner ring,
A tapered roller interposed between the outer ring and the inner ring;
A cage guided radially by the inner circumference of the outer ring;
With
The cage divides the first annular portion, the second annular portion having an outer diameter larger than that of the first annular portion, and the first annular portion and the second annular portion into pockets. And a pillar portion,
The tapered roller bearing, wherein the second annular portion has a flange protruding to the inner ring side. 前記第２環状部が、内周全周に連なった溝を有し、前記鍔が、前記溝の溝壁を兼ねるように形成されている請求項１に記載の円すいころ軸受。   2. The tapered roller bearing according to claim 1, wherein the second annular portion has a groove continuous with the entire inner periphery, and the flange is formed so as to also serve as a groove wall of the groove. 前記第１環状部及び前記２環状部の少なくとも一方が、前記外輪の内周に周方向にすべり接触し得る被案内面と、前記被案内面を周方向に分断するように凹んだ油溝とを有する請求項１又は２に記載の円すいころ軸受。   A guided surface in which at least one of the first annular portion and the second annular portion can slide in contact with the inner periphery of the outer ring in the circumferential direction, and an oil groove recessed so as to divide the guided surface in the circumferential direction The tapered roller bearing according to claim 1, wherein: 請求項１から３のいずれか１項に記載の一対の円すいころ軸受と、一対の前記内輪間の軸方向間隔を保つ内輪間座と、を備え、
前記内輪間座が、一対の前記内輪のそれぞれに向かって次第に外径を大きくした外径面を有する遊星軸受装置。 A pair of tapered roller bearings according to any one of claims 1 to 3, and an inner ring spacer that maintains an axial interval between the pair of inner rings,
A planetary bearing device in which the inner ring spacer has an outer diameter surface that gradually increases in outer diameter toward each of the pair of inner rings. 前記外輪の側面に軸方向に当てる間座を備え、
前記間座が、前記外輪に向かって次第に内径を大きくした内径面を有する請求項４に記載の遊星軸受装置。 A spacer that is axially applied to the side surface of the outer ring,
The planetary bearing device according to claim 4, wherein the spacer has an inner diameter surface that gradually increases in inner diameter toward the outer ring. 一対の前記外輪間の軸方向間隔を保つ外輪間座を備え、
前記外輪間座が、前記一対の外輪に挟まれた基部と、潤滑油を掻き上げるように前記基部から突き出た突起部とを有する請求項４又は５に記載の遊星軸受装置。 An outer ring spacer that maintains an axial interval between the pair of outer rings;
6. The planetary bearing device according to claim 4, wherein the outer ring spacer has a base portion sandwiched between the pair of outer rings and a protrusion protruding from the base portion so as to scoop up lubricating oil. 前記基部が、内周に形成された螺旋溝を有する請求項６に記載の遊星軸受装置。   The planetary bearing device according to claim 6, wherein the base has a spiral groove formed on an inner periphery.
JP2015122862A 2015-06-18 2015-06-18 Conical roller bearing and planetary bearing device Pending JP2017008987A (en)

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