JP2011043207A - Lubricating device for rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enable a structure which can circulate a lubricating oil inside a double row cylindrical roller bearing 3 to be made small and light in weight and to be obtained at low cost. <P>SOLUTION: The lower end portion of an annular centrifugal flow initiation member 42 is immersed in the lubricating oil reserved in a lubricating oil reservoir 37 at the bottom portion of a bearing box 1. A through hole 14 of an outer ring spacer 6 provided at the intermediate part of the double row cylindrical roller bearing 3 is used as an oil supply passage. Also, a return passage 40a is provided between the centrifugal flow initiation member 42 and the lubricating oil reservoir 37. The centrifugal flow initiation member 42 is externally fitted and supported on a nut 24b which presses an inner ring 4 constituting the double row cylindrical roller bearing 3 in a state where it rotates with the nut 24b. With the rotation of the centrifugal flow initiation member 42, the flow of the lubricating oil circulating through the outside row cylindrical rollers 7, 7 portions is initiated. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

この発明は、鉄道車両の車軸を台車に対して回転自在に支持する為の転がり軸受の潤滑装置の改良に関する。具体的には、転がり軸受の内部に潤滑油を効率良く循環させられる構造を、小型且つ軽量に構成でき、しかも低コストで得られる様にするものである。   The present invention relates to an improvement in a rolling bearing lubrication device for rotatably supporting an axle of a railway vehicle with respect to a carriage. Specifically, a structure capable of efficiently circulating lubricating oil inside a rolling bearing can be configured to be small and lightweight, and can be obtained at low cost.

鉄道車両の車軸は台車に保持した軸受箱に対して、複列円すいころ軸受、或いは複列円筒ころ軸受等の転がり軸受により、回転自在に支持している。この様な用途に使用される転がり軸受は、例えば前記鉄道車両が新幹線等の高速車両である場合には、非常に大きなラジアル荷重を支承しつつ高速で回転する。この為、前記転がり軸受の信頼性及び耐久性を確保する為には、この転がり軸受の内部に十分量の潤滑油を循環させる潤滑装置が必要になる。この為従来から、例えば特許文献１、２に記載されている様に、軸受箱の内部に潤滑油溜りを設けると共に、転がり軸受の下部をこの潤滑油溜りに貯溜した潤滑油中に浸漬し、この潤滑油をこの転がり軸受の内部を通じて循環させる潤滑装置が知られている。図７は、この様な潤滑装置を組み込んだ、鉄道車両の車軸支持用の転がり軸受装置の、従来構造の１例を示している。   An axle of a railway vehicle is rotatably supported by a rolling bearing such as a double-row tapered roller bearing or a double-row cylindrical roller bearing with respect to a bearing box held on the carriage. For example, when the railway vehicle is a high-speed vehicle such as a bullet train, the rolling bearing used for such an application rotates at a high speed while supporting a very large radial load. For this reason, in order to ensure the reliability and durability of the rolling bearing, a lubricating device that circulates a sufficient amount of lubricating oil inside the rolling bearing is required. For this reason, conventionally, as described in Patent Documents 1 and 2, for example, a lubricating oil reservoir is provided inside the bearing box, and the lower part of the rolling bearing is immersed in the lubricating oil stored in the lubricating oil reservoir, Lubricating devices that circulate this lubricating oil through the inside of this rolling bearing are known. FIG. 7 shows an example of a conventional structure of a rolling bearing device for supporting an axle of a railway vehicle incorporating such a lubrication device.

この従来構造は、軸受箱１の内径側に車軸２の端部を、複列円筒ころ軸受３により、回転自在に支持している。この複列円筒ころ軸受３は、１個の内輪４と、１対の外輪５、５と、１個の外輪間座６と、複数個の円筒ころ７、７とを備える。このうちの内輪４は、内輪本体８と鍔輪９とを組み合わせて成る。このうちの内輪本体８は、一端部（図７の右端部）外周面に外向フランジ状の内輪鍔１０を形成すると共に、外周面の残部を、複列円筒状の内輪軌道１１としている。又、前記鍔輪９は、前記内輪鍔１０と同等の外径寸法を有する円輪状としている。一方、前記両外輪５、５は、それぞれの中間部内周面を円筒状の外輪軌道１２、１２とし、それぞれの両端部内周面に、内向フランジ状の外輪鍔１３、１３を形成している。又、前記外輪間座６は、前記両外輪５、５の互いに対向する端面同士の間に挟持している。この外輪間座６は、円環状で、円周方向に関する複数個所に、それぞれがこの外輪間座６を径方向に貫通してこの外輪間座６の内外両周面同士を連通させる、通孔１４、１４を形成している。これら各通孔１４、１４が、前記複列円筒ころ軸受３の内部に潤滑油を送り込む為の給油通路を構成する。更に、前記各円筒ころ７、７は、保持器１５、１５により転動自在に保持された状態で、前記内輪軌道１１と前記両外輪軌道１２、１２との間に、両列毎に複数個ずつ設けられている。   In this conventional structure, the end portion of the axle 2 is rotatably supported by the double row cylindrical roller bearing 3 on the inner diameter side of the bearing housing 1. This double row cylindrical roller bearing 3 includes one inner ring 4, a pair of outer rings 5, 5, one outer ring spacer 6, and a plurality of cylindrical rollers 7, 7. Of these, the inner ring 4 is formed by combining an inner ring main body 8 and a collar ring 9. Of these, the inner ring main body 8 is formed with an outward flange-shaped inner ring rod 10 on the outer peripheral surface of one end portion (the right end portion in FIG. 7), and the remaining portion of the outer peripheral surface is a double-row cylindrical inner ring track 11. The saddle ring 9 has an annular shape having an outer diameter equivalent to that of the inner ring collar 10. On the other hand, both the outer rings 5 and 5 have cylindrical outer ring raceways 12 and 12 at the inner peripheral surfaces of the intermediate portions, and outer flanges 13 and 13 having inward flange shapes are formed on the inner peripheral surfaces of both ends. The outer ring spacer 6 is sandwiched between the end faces of the outer rings 5, 5 facing each other. The outer ring spacer 6 is annular and has a plurality of holes in the circumferential direction, each of which penetrates the outer ring spacer 6 in the radial direction and communicates the inner and outer peripheral surfaces of the outer ring spacer 6 with each other. 14 and 14 are formed. These through holes 14, 14 constitute an oil supply passage for feeding lubricating oil into the double row cylindrical roller bearing 3. Further, a plurality of cylindrical rollers 7 and 7 are provided for each row between the inner ring raceway 11 and the outer ring raceways 12 and 12 in a state in which the cylindrical rollers 7 and 7 are rotatably held by cages 15 and 15. It is provided one by one.

上述の様な複列円筒ころ軸受３は、前記軸受箱１の内周面と前記車軸２の端部外周面との間に設けている。先ず、この複列円筒ころ軸受３の外輪５、５と外輪間座６とを、前記軸受箱１に内嵌した状態で、この軸受箱１の内周面の内端寄り（図示しない車輪本体寄りで、図７の右寄り）部分に形成した段部１６と、前記軸受箱１の外端（図示しない車輪本体と反対側の端で、図７の左端）開口部に内嵌した前蓋１７の円筒部１８の先端縁との間で挟持している。又、Ｏリング１９により、この円筒部１８と前記軸受箱１の内周面との嵌合部の油密保持を図っている。尚、前記前蓋１７の中央部に設けた開口部２０は、点検や給油の為のもので、運転時には、図示しないゴムキャップにより塞いでおく。   The double-row cylindrical roller bearing 3 as described above is provided between the inner peripheral surface of the bearing housing 1 and the outer peripheral surface of the end portion of the axle 2. First, in a state where the outer rings 5 and 5 and the outer ring spacer 6 of the double row cylindrical roller bearing 3 are fitted in the bearing box 1, they are close to the inner end of the inner peripheral surface of the bearing box 1 (wheel body (not shown)). A step 16 formed in a portion near the right side of FIG. 7 and a front lid 17 fitted into an opening of the outer end of the bearing housing 1 (the left end in FIG. 7 on the side opposite to the wheel body (not shown)). It is pinched between the front-end edge of the cylindrical part 18 of this. Further, the O-ring 19 is used to keep the fitting portion between the cylindrical portion 18 and the inner peripheral surface of the bearing housing 1 oil tight. The opening 20 provided in the central portion of the front lid 17 is for inspection and refueling, and is closed with a rubber cap (not shown) during operation.

又、前記内輪４は、油切り２１と共に、前記車軸２の端部寄り部分に外嵌固定している。この油切り２１は、全体を段付円筒状としたもので、前記車軸２の中間部端部寄り部分に形成した、軸端に向かうに従って外径が小さくなる方向に傾斜した肩部２２に、異物の浸入を十分に防止できる程度に隙間なく外嵌している。又、前記車軸２の端部に形成した雄ねじ部２３に円環状のナット２４を螺着している。前記内輪４は、前記内輪本体８の内端面を前記油切り２１の外端面に突き当てると共に、前記ナット２４により前記鍔輪９を、前記内輪本体８の外端面に向け抑え付ける事で、前記車軸２の端部に外嵌固定している。尚、前記車軸２の端部で前記ナット２４から突出した部分には、回り止めリング２５を外嵌している。この回り止めリング２５は、内周縁の１乃至複数個所に突設した突片２６と、前記車軸２の端部外周面に形成した凹溝２７とを係合させる事により、この車軸２に対する回転を阻止している。更に、前記回り止めリング２５を挿通した複数本のボルト２８を、前記ナット２４の一部に軸方向に形成したねじ孔２９、２９（本発明の実施の形態を示す図４参照）に螺合し更に締め付けている。この構成により、前記ナット２４の緩み止めを図っている。   Further, the inner ring 4 is externally fitted and fixed to the end portion of the axle 2 together with the oil drain 21. The oil drainer 21 has a stepped cylindrical shape as a whole, and is formed in a portion closer to the end of the intermediate portion of the axle 2, and is formed on a shoulder 22 inclined in a direction in which the outer diameter decreases toward the shaft end. It fits outside enough to prevent foreign objects from entering. An annular nut 24 is screwed to a male screw portion 23 formed at the end of the axle 2. The inner ring 4 abuts the inner end surface of the inner ring main body 8 against the outer end surface of the oil drainer 21, and suppresses the saddle wheel 9 toward the outer end surface of the inner ring main body 8 by the nut 24. It is fitted and fixed to the end of the axle 2. In addition, a detent ring 25 is externally fitted to a portion of the end portion of the axle 2 that protrudes from the nut 24. The rotation-preventing ring 25 is rotated with respect to the axle 2 by engaging a projecting piece 26 projecting from one or a plurality of locations on the inner peripheral edge with a concave groove 27 formed on the outer peripheral surface of the end of the axle 2. Is blocking. Further, a plurality of bolts 28 inserted through the locking ring 25 are screwed into screw holes 29 and 29 (see FIG. 4 showing the embodiment of the present invention) formed in a part of the nut 24 in the axial direction. And it is tightened further. With this configuration, the nut 24 is prevented from loosening.

前記軸受箱１の内端開口部と前記油切り２１との間に、前記車軸２の中央側から順番に、ラビリンスシール３０と、接触式のシールリング３１とを設けている。これらラビリンスシール３０及びシールリング３１を設ける為、前記軸受箱１の内端部に、後蓋３２を組み付けている。これら軸受箱１と後蓋３２との嵌合部はＯリング３３によりシールしている。又、この後蓋３２の内周面に設けた断面Ｌ字形の固定側突条３４と、前記油切り２１の内端部外周面に設けた断面Ｌ字形の回転側突条３５とを近接対向させて、前記ラビリンスシール３０を構成している。又、上記後蓋３２の内端寄り部分の下端部には、外部からこのラビリンスシール３０の内部に浸入した雨水等の異物を、再び外部に排出する為の排出孔４６を設けている。又、前記シールリング３１の芯金を前記後蓋３２の外端部に内嵌固定すると共に、このシールリング３１の弾性材を、前記油切り２１の中間部外周面に摺接させている。更に、この油切り２１の外端部と前記内輪４の内端面との間に、円輪状のスリンガ３６を挟持固定している。   A labyrinth seal 30 and a contact-type seal ring 31 are provided between the inner end opening of the bearing housing 1 and the oil drainer 21 in order from the center side of the axle 2. In order to provide the labyrinth seal 30 and the seal ring 31, a rear lid 32 is assembled to the inner end portion of the bearing housing 1. The fitting portion between the bearing box 1 and the rear lid 32 is sealed by an O-ring 33. Further, a fixed side protrusion 34 having an L-shaped cross section provided on the inner peripheral surface of the rear lid 32 and a rotation side protrusion 35 having an L-shaped cross section provided on the outer peripheral surface of the inner end portion of the oil drain 21 are opposed to each other. Thus, the labyrinth seal 30 is configured. In addition, a discharge hole 46 is provided at the lower end of the rear lid 32 near the inner end to discharge foreign matter such as rainwater that has entered the labyrinth seal 30 from the outside to the outside. Further, the core metal of the seal ring 31 is fitted and fixed to the outer end portion of the rear lid 32, and the elastic material of the seal ring 31 is brought into sliding contact with the outer peripheral surface of the intermediate portion of the oil drainer 21. Further, an annular slinger 36 is sandwiched and fixed between the outer end portion of the oil drain 21 and the inner end surface of the inner ring 4.

前記軸受箱１のうち、組み付け状態で車体の重量を支承しない非負荷圏である下端部に、潤滑油溜り３７を設けている。この潤滑油溜り３７は、前記軸受箱１の下端部の軸方向中間部を両側部分よりも下方に凹ませて成るもので、中央部に設けたドレン孔３８を、ねじ蓋３９により塞いでいる。又、前記軸受箱１の下端部内周面で前記潤滑油溜り３７を軸方向両側から挟む部分と、前記両外輪５、５の下端部外周面とを互いに離隔させて、当該部分をそれぞれ戻り通路４０ａ、４０ｂとしている。運転時には、前記潤滑油溜り３７を含む、前記軸受箱１の下部に、前記複列円筒ころ軸受３を潤滑する為に適切な潤滑油を貯溜する。この潤滑油の量は、液面が前記両外輪５、５に形成した外輪鍔１３の内周面の下端位置よりも少し上側に存在する様に規制する。従って、前記複列円筒ころ軸受３の下端部内側には、前記軸受箱１の下部に貯溜された潤滑油が入り込む。   A lubricating oil reservoir 37 is provided at a lower end portion of the bearing housing 1 that is a non-load zone that does not support the weight of the vehicle body in the assembled state. This lubricating oil reservoir 37 is formed by denting the axially intermediate portion of the lower end portion of the bearing housing 1 below the both side portions, and a drain hole 38 provided in the central portion is closed by a screw lid 39. . Further, a portion sandwiching the lubricating oil reservoir 37 from both sides in the axial direction on the inner peripheral surface of the lower end portion of the bearing housing 1 and the outer peripheral surfaces of the lower end portions of the outer rings 5, 5 are separated from each other, and the portions are respectively connected to the return passages. 40a and 40b. During operation, appropriate lubricating oil is stored in the lower portion of the bearing housing 1 including the lubricating oil reservoir 37 in order to lubricate the double row cylindrical roller bearing 3. The amount of the lubricating oil is regulated so that the liquid level exists slightly above the lower end position of the inner peripheral surface of the outer ring rod 13 formed on the outer rings 5 and 5. Accordingly, the lubricating oil stored in the lower portion of the bearing housing 1 enters the lower end of the double row cylindrical roller bearing 3.

上述の図７に示した構造の運転時には、前記車軸２の回転に伴って惹起される潤滑油の流れにより、前記複列円筒ころ軸受３の内部に潤滑油が流通する。具体的には、前記外輪間座６の通孔１４から前記複列に配置された円筒ころ７、７同士の間に入り込んだ潤滑油が、これら各円筒ころ７、７を設置した空間を軸方向に流れ、前記複列円筒ころ軸受３の両端開口から排出される。更に、この両端開口から排出された潤滑油は、前記両戻り通路４０ａ、４０ｂを通じて前記潤滑油溜り３７に回収され、再び前記通孔１４を通じて、前記複列円筒ころ軸受３の内部に送り込まれる。   During the operation of the structure shown in FIG. 7 described above, the lubricating oil flows through the double row cylindrical roller bearing 3 due to the flow of the lubricating oil caused by the rotation of the axle 2. Specifically, the lubricating oil that has entered between the cylindrical rollers 7, 7 arranged in the double row from the through-hole 14 of the outer ring spacer 6 rotates in the space where the cylindrical rollers 7, 7 are installed. It flows in the direction and is discharged from the opening at both ends of the double row cylindrical roller bearing 3. Further, the lubricating oil discharged from the opening at both ends is collected in the lubricating oil reservoir 37 through the return passages 40a and 40b, and is sent again into the double row cylindrical roller bearing 3 through the through hole 14.

上述の様な転がり軸受用潤滑装置の機能を十分に果たさせる為には、前記複列円筒ころ軸受３の内部を流通する潤滑油の量を確保する必要がある。例えば特許文献１に記載されている様に、転がり軸受が複列円すいころ軸受である場合には、複列円すいころ軸受特有のポンプ作用により、転がり軸受の内部に十分量の潤滑油を循環させる事ができる。これに対して、図７に示す様な複列円筒ころ軸受３の場合には、転動体である円筒ころ７、７の中心軸と回転軸である車軸２の中心軸とが平行である為、前記複列円筒ころ軸受３自体は、殆どポンプ作用をする事がない。この為、そのままではこの複列円筒ころ軸受３の内部に十分な潤滑油を流通させる事ができない。図７に示した構造では、スリンガ３６の回転に伴って潤滑油の流れが惹起されるが、その流れは、主として内側（図７の右側）の列の円筒ころ７、７部分を流通する。外側（図７の左側）の列の円筒ころ７、７部分には、必ずしも十分量の潤滑油が流通しない。これに対して、例えば、鉄道車両の車軸を台車に対して回転自在に支持する為の複列転がり軸受の場合、車軸から加わるモーメントの影響で、外側列の負荷が内側列の負荷よりも大きくなる。従って、新幹線等の高速鉄道車両の如く、使用条件が厳しい場合には、図７に示す様な構造では十分な耐久性を確保できなくなる可能性がある。   In order to sufficiently perform the function of the rolling bearing lubrication device as described above, it is necessary to secure an amount of lubricating oil flowing through the inside of the double row cylindrical roller bearing 3. For example, as described in Patent Document 1, when the rolling bearing is a double-row tapered roller bearing, a sufficient amount of lubricating oil is circulated inside the rolling bearing by a pump action unique to the double-row tapered roller bearing. I can do things. On the other hand, in the case of the double row cylindrical roller bearing 3 as shown in FIG. 7, the central axis of the cylindrical rollers 7 and 7 that are rolling elements and the central axis of the axle 2 that is a rotating shaft are parallel. The double row cylindrical roller bearing 3 itself hardly performs a pumping action. For this reason, sufficient lubricating oil cannot be circulated inside the double row cylindrical roller bearing 3 as it is. In the structure shown in FIG. 7, the flow of the lubricating oil is caused as the slinger 36 rotates, and the flow mainly flows through the cylindrical rollers 7 and 7 in the inner row (the right side in FIG. 7). A sufficient amount of lubricating oil does not necessarily flow through the cylindrical rollers 7 and 7 in the outer row (left side in FIG. 7). On the other hand, for example, in the case of a double row rolling bearing for rotatably supporting the axle of a railway vehicle with respect to the carriage, the load on the outer row is larger than the load on the inner row due to the moment applied from the axle. Become. Therefore, when the use conditions are severe, such as a high-speed railway vehicle such as a Shinkansen, there is a possibility that sufficient durability cannot be secured with the structure shown in FIG.

この様な事情に鑑みて、特許文献２には、図８に示す様に、鍔輪９ａを大型化して、潤滑油の流れを惹起させる為の遠心流惹起部材を構成した構造が記載されている。この従来構造の第２例の場合には、前記鍔輪９ａの軸方向寸法を大きくして、この鍔輪９ａの外半部を外側の外輪５の外端面よりも外方に突出させている。そして、この突出した部分の外周面に、それぞれが外向フランジ状である、複数の遠心流惹起板部４１、４１を形成している。運転時には、前記鍔輪９ａの回転に伴って、これら遠心流惹起板部４１、４１が潤滑油の流れを惹起させる。即ち、運転時にはこれら遠心流惹起板部４１、４１が、軸受箱１の下部に貯溜された潤滑油の一部にそれぞれの下部を漬からせた状態のまま回転する。そして、遠心力に基づいて前記各遠心流惹起板部４１、４１の近傍部分に、これら各遠心流惹起板部４１、４１の内径側から外径側に向かい、更に前記各遠心流惹起板部４１、４１の外周縁よりもこれら各遠心流惹起板部４１、４１の径方向外側に向かう潤滑油の流れを惹起させる。これに伴って、複列円筒ころ軸受３ａの外端開口近傍部分の圧力が低下し、複列に配置された円筒ころ７、７の間部分からこの外端開口近傍部分に向かう、潤滑油の流れが惹起される。又、前記複列円筒ころ軸受３ａの外端開口に対向する内側の遠心流惹起板部４１の回転に伴って、この遠心流惹起板部４１の内側に沿って径方向外側に流れる気流が惹起される。そして、外側列の円筒ころ７、７部分に、軸方向に関して内側から外側に向かう気流が惹起され、この気流に乗って潤滑油の飛沫が送られる。この結果、外側列の円筒ころ７、７部分に関しても、十分量の潤滑油を流通させられる。   In view of such circumstances, Patent Document 2 describes a structure in which a centrifugal flow elevating member for enlarging the flow of the lubricating oil is configured as shown in FIG. Yes. In the case of the second example of this conventional structure, the axial dimension of the saddle wheel 9a is increased so that the outer half of the saddle wheel 9a protrudes outward from the outer end face of the outer outer ring 5. . A plurality of centrifugal flow-inducing plate portions 41, 41 each having an outward flange shape are formed on the outer peripheral surface of the protruding portion. During operation, the centrifugal flow-inducing plate portions 41 and 41 cause a flow of lubricating oil as the saddle wheel 9a rotates. In other words, during operation, the centrifugal flow-inducing plate portions 41 and 41 rotate with their lower portions immersed in a part of the lubricating oil stored in the lower portion of the bearing box 1. Then, on the basis of the centrifugal force, the centrifugal flow inducing plate portions 41, 41 are arranged in the vicinity of the centrifugal flow inducing plate portions 41, 41 from the inner diameter side to the outer diameter side, and further in the respective centrifugal flow inducing plate portions. The flow of the lubricating oil is caused to be directed to the radially outer side of each of the centrifugal flow inducing plate portions 41 and 41 from the outer peripheral edges of the 41 and 41. Along with this, the pressure in the vicinity of the outer end opening of the double row cylindrical roller bearing 3a decreases, and the lubricating oil flowing from the portion between the cylindrical rollers 7 and 7 arranged in the double row to the vicinity of the outer end opening The flow is triggered. Further, along with the rotation of the inner centrifugal flow inducing plate portion 41 facing the outer end opening of the double row cylindrical roller bearing 3a, an air flow flowing radially outward along the inner side of the centrifugal flow inducing plate portion 41 is caused. Is done. An air flow from the inside toward the outside in the axial direction is induced in the cylindrical rollers 7 and 7 in the outer row, and a splash of lubricating oil is sent along the air flow. As a result, a sufficient amount of lubricating oil can be circulated also for the cylindrical rollers 7 and 7 in the outer row.

この様な特許文献２に記載された従来構造の第２例の場合、潤滑油の流通量確保の面からは十分な性能を得られるが、小型・軽量化、低コスト化の面からは改良の余地がある。即ち、前記遠心流惹起板部４１、４１を設けるべく、前記鍔輪９ａの軸方向寸法を大きくする分、車軸２の軸方向寸法も大きくする必要を生じる。この為、これら鍔輪９ａ及び車軸２の大型化、重量増大が避けられず、小型・軽量化を図りにくい。又、前記遠心流惹起板部４１、４１を前記鍔輪９ａと一体に造る以上、この遠心流惹起板部４１、４１も、軸受鋼等の硬質金属製とする必要がある。硬質金属により、この遠心流惹起板部４１、４１を一体化した前記鍔輪９ａを造る事は面倒で、低コスト化の妨げとなる。   In the case of the second example of the conventional structure described in Patent Document 2 as described above, sufficient performance can be obtained from the aspect of securing the circulation amount of the lubricating oil, but improvement from the viewpoint of reduction in size, weight, and cost. There is room for. That is, in order to provide the centrifugal flow-inducing plate portions 41, 41, it is necessary to increase the axial dimension of the axle 2 as the axial dimension of the saddle wheel 9a is increased. For this reason, the enlargement and weight increase of these saddle wheel 9a and axle 2 cannot be avoided, and it is difficult to reduce the size and weight. In addition, since the centrifugal flow inducing plate portions 41 and 41 are integrally formed with the eaves 9a, the centrifugal flow inducing plate portions 41 and 41 also need to be made of a hard metal such as bearing steel. It is troublesome to make the ring 9a in which the centrifugal flow-inducing plate portions 41, 41 are integrated by using a hard metal, which hinders cost reduction.

小型・軽量化のみを図るのであれば、図９に示す様に、ナット２４ａの外周面に遠心流惹起板部４１ａ、４１ａを形成する事も考えられる。この様に構成すれば、車軸２の軸方向寸法も大きくする必要がなくなり、小型・軽量化を図れるが、低コスト化を図る面からは、必ずしも十分とは言えない。即ち、前記ナット２４ａは、前記鍔輪９ａ（図８参照）程は硬い材料で造る必要はない為、加工コストに関しても、前記従来構造の第２例よりも低く抑えられる。但し、前記ナット２４ａにしても、或る程度硬い材料により造る必要があり、前記各遠心流惹起板部４１ａ、４１ａの加工を十分容易に行えるとは言えず、低コスト化を図る面からは、依然として改良の余地がある。   If only a reduction in size and weight is to be achieved, it is conceivable to form centrifugal flow-inducing plate portions 41a and 41a on the outer peripheral surface of the nut 24a as shown in FIG. With this configuration, it is not necessary to increase the axial dimension of the axle 2 and the size and weight can be reduced, but this is not necessarily sufficient from the viewpoint of cost reduction. That is, the nut 24a does not need to be made of a material as hard as the collar 9a (see FIG. 8), so that the processing cost can be kept lower than the second example of the conventional structure. However, the nut 24a also needs to be made of a somewhat hard material, and it cannot be said that the processing of the centrifugal flow-inducing plate portions 41a and 41a can be performed sufficiently easily. There is still room for improvement.

特開２００６−８３９４５号公報JP 2006-83945 A 特開２００９−４１７２８号公報JP 2009-41728 A

本発明は、上述の様な事情に鑑みて、複列円筒ころ軸受等の転がり軸受の内部に潤滑油を効率良く循環させられる構造を、小型且つ軽量に構成でき、しかも低コストで得られる様にすべく発明したものである。   In view of the circumstances as described above, the present invention can be configured in a compact and lightweight structure capable of efficiently circulating lubricating oil inside a rolling bearing such as a double row cylindrical roller bearing, and can be obtained at low cost. The invention was invented.

本発明の転がり軸受用潤滑装置は、前述の特許文献２に記載されて従来から知られている転がり軸受用潤滑装置と同様に、潤滑油溜りと、給油通路と、遠心流惹起部材と、戻り通路とを備える。
このうちの潤滑油溜りは、軸受箱の如き回転しないハウジングの内径側に、車軸の如き回転軸を支持する為の、複列円筒ころ軸受の如き転がり軸受の内部に潤滑油を循環させる為、前記ハウジングの下端部内側に設けられている。
又、前記給油通路は、前記転がり軸受を構成する複数個の転動体の列を挟んで、当該列の軸方向片側に設けられたもので、外径側を前記潤滑油溜りに貯溜された潤滑油内に開口させると共に、内径側を前記転がり軸受の内部に通じさせている。
又、前記遠心流惹起部材は、円環状で、前記回転軸と共に回転する状態で前記各転動体の列を挟んで軸方向他側に設けられたもので、下部外径寄り部分を、前記潤滑油溜りに貯溜された潤滑油中に浸漬させている。
更に、前記戻り通路は、前記遠心流惹起部材と前記潤滑油溜りとの間に設けられている。 The rolling bearing lubrication device of the present invention is similar to the rolling bearing lubrication device described in the above-mentioned Patent Document 2 and has been conventionally known, and includes a lubricating oil reservoir, an oil supply passage, a centrifugal flow inducing member, And a passage.
Of these, the lubricating oil reservoir is used to support the rotating shaft such as the axle on the inner diameter side of the non-rotating housing such as the bearing box, and to circulate the lubricating oil inside the rolling bearing such as the double row cylindrical roller bearing. It is provided inside the lower end of the housing.
The oil supply passage is provided on one axial side of the row of the plurality of rolling elements constituting the rolling bearing, and the outer diameter side of the lubrication passage is stored in the lubricating oil reservoir. While being opened in oil, the inner diameter side is connected to the inside of the rolling bearing.
Further, the centrifugal flow inducing member is annular, and is provided on the other side in the axial direction with the row of the rolling elements in a state of rotating together with the rotating shaft. It is immersed in the lubricating oil stored in the oil sump.
Further, the return passage is provided between the centrifugal flow inducing member and the lubricating oil reservoir.

特に、本発明の転がり軸受用潤滑装置に於いては、前記遠心流惹起部材が、前記転がり軸受を構成する内輪の軸方向他側に隣接する状態で設けられて前記回転軸と共に回転する円環状部材に、この円環状部材と共に回転する状態で外嵌支持されている。
この様な本発明の転がり軸受用潤滑装置を実施する場合、具体的には、請求項２に記載した発明の様に、前記回転軸を鉄道車両用の車軸とし、前記ハウジングを軸受箱とする。又、前記転がり軸受を、外周面に複列円筒状の内輪軌道を有する内輪と、それぞれの内周面に円筒状の外輪軌道を有する１対の外輪と、これら両外輪同士の間に挟持された外輪間座と、前記両内輪軌道と前記両外輪軌道との間に、両列毎に複数個ずつ転動自在に設けられた、それぞれが転動体である円筒ころとを備えたものとする。又、前記給油通路を、前記外輪間座の一部を径方向に貫通する状態で設けられた通孔とする。更に、前記環状部材を、前記車軸に対して前記内輪を固定する為のナットとする。そして、このナットに遠心流惹起部材を外嵌した状態で、これらナットの外周面と遠心流惹起部材の内周面とを非円形係合させる。 Particularly, in the rolling bearing lubrication device of the present invention, the centrifugal flow inducing member is provided in a state adjacent to the other axial side of the inner ring constituting the rolling bearing and rotates together with the rotary shaft. The member is externally supported so as to rotate together with the annular member.
When implementing such a rolling bearing lubrication device of the present invention, specifically, as in the invention described in claim 2, the rotating shaft is an axle for a railway vehicle and the housing is a bearing box. . Further, the rolling bearing is sandwiched between these outer rings, an inner ring having a double-row cylindrical inner ring raceway on an outer peripheral surface, a pair of outer rings having a cylindrical outer ring raceway on each inner peripheral surface. A plurality of outer ring spacers, and a plurality of cylindrical rollers provided between the inner ring raceways and the outer ring raceways, each being a rolling element. . Further, the oil supply passage is a through hole provided in a state of passing through a part of the outer ring spacer in the radial direction. Further, the annular member is a nut for fixing the inner ring to the axle. Then, the outer peripheral surface of these nuts and the inner peripheral surface of the centrifugal flow inducing member are non-circularly engaged in a state where the centrifugal flow inducing member is fitted on the nut.

上述の様に構成する本発明の転がり軸受用潤滑装置によれば、複列円筒ころ軸受等の転がり軸受の内部に潤滑油を効率良く循環させられる構造を、小型且つ軽量に構成でき、しかも低コストで得られる。
先ず、潤滑油を効率良く循環させられる事は、回転軸の回転に伴って遠心流惹起部材が、転動体の列の軸方向他側部分に存在する潤滑油に、遠心流、即ち、遠心流惹起部材の内径側から外径側に向かう潤滑油の流れを惹起し、前記転動体の列の軸方向片側部分から他側部分に向けて潤滑油の流れを惹起させる事により実現できる。この点に関しては、前述した特許文献２に記載された従来構造の場合と同様である。 According to the rolling bearing lubrication device of the present invention configured as described above, a structure capable of efficiently circulating lubricating oil inside a rolling bearing such as a double row cylindrical roller bearing can be configured to be small and lightweight, and low Obtained at a cost.
First, the fact that the lubricating oil can be circulated efficiently is that the centrifugal flow-inducing member is moved into the lubricating oil existing on the other side in the axial direction of the row of rolling elements, that is, the centrifugal flow, that is, the centrifugal flow. This can be realized by inducing a flow of lubricating oil from the inner diameter side to the outer diameter side of the pulling member, and inducing a flow of the lubricating oil from one axial portion of the row of rolling elements toward the other portion. This is the same as the case of the conventional structure described in Patent Document 2 described above.

又、小型且つ軽量に構成できる事は、前記遠心流惹起部材を、ナットの如く、既存の環状部材の周囲に外嵌支持する事により実現できる。即ち、これら遠心流惹起部材と環状部材とを径方向に重畳させた状態で設ける為、この遠心流惹起部材を設置する事に伴って、鍔輪や回転軸等、一部の部材の軸方向寸法を大きくする必要がなくなり、優れた潤滑性能を有する構造を、小型且つ軽量に構成できる。この点に関しては、前述の図９に示した、先に考えた構造の場合と同様である。   Further, the fact that the structure can be made small and lightweight can be realized by externally supporting the centrifugal flow-inducing member around an existing annular member such as a nut. In other words, since the centrifugal flow inducing member and the annular member are provided in a state of being superimposed in the radial direction, the axial direction of some members such as a collar and a rotating shaft is provided along with the installation of the centrifugal flow inducing member. It is not necessary to increase the size, and a structure having excellent lubrication performance can be configured to be small and light. This is the same as the case of the structure previously considered shown in FIG.

更に、低コストで得られる事は、前記特許文献２に記載された従来構造の様に、硬質金属製の鍔輪や、或る程度の強度を必要とするナットに遠心流惹起板部を加工する必要がない事により図れる。前記遠心流惹起部材は、回転に伴う遠心力や、潤滑油に浸漬する事に伴って発生する摩擦抵抗に基づく応力、運転に伴って発生する振動等により破損しない程度の強度があれば足りる。従って、軸受鋼の如き硬質金属製とする必要はなく、耐油性を有する合成樹脂や、銅、アルミニウム等の、比較的軟質の金属により造る事ができて、低コスト化を図れる。   Furthermore, what can be obtained at a low cost is the processing of the centrifugal flow induction plate portion on a hard metal ring or a nut that requires a certain degree of strength, as in the conventional structure described in Patent Document 2. You can do it by not having to do it. The centrifugal flow inducing member only needs to be strong enough not to be damaged by centrifugal force accompanying rotation, stress based on frictional resistance generated by being immersed in lubricating oil, vibration generated by operation, and the like. Therefore, it is not necessary to use a hard metal such as bearing steel, and it can be made of a relatively soft metal such as oil-resistant synthetic resin, copper, or aluminum, thereby reducing the cost.

本発明の実施の形態の１例を示す断面図。Sectional drawing which shows one example of embodiment of this invention. 図１のイ部拡大図。FIG. 同ロ部拡大図。FIG. ナットを軸方向から見た図。The figure which looked at the nut from the axial direction. 遠心流惹起部材を軸方向から見た図（Ａ）、及び、（Ａ）のハ−ハ断面図（Ｂ）。The figure (A) which looked at the centrifugal flow induction member from the axial direction, and the ha sectional view (B) of (A). 遠心流惹起部材の形状の６例を示す半部断面図。Sectional drawing of the half part which shows six examples of the shape of a centrifugal flow induction member. 従来構造の第１例を示す断面図。Sectional drawing which shows the 1st example of a conventional structure. 同第２例を示す断面図。Sectional drawing which shows the 2nd example. 本発明に先立って考えた構造の１例を示す断面図。Sectional drawing which shows an example of the structure considered prior to this invention.

図１〜５は、本発明の実施の形態の１例を示している。尚、本例の特徴は、外側（図１の左側）の列の転動体設置部分に潤滑油を流通させる為の遠心流惹起部材４２の設置部分の構造にある。その他の部分の構造及び作用は、前述の図７〜８に示した従来構造と同様であるから、同等部分には同一符号を付して重複する説明を省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。   1 to 5 show an example of an embodiment of the present invention. The feature of this example is the structure of the installation part of the centrifugal flow eliciting member 42 for circulating the lubricating oil to the rolling element installation part of the outer (left side in FIG. 1) row. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 7 to 8 described above, the same parts are denoted by the same reference numerals, and redundant description is omitted or simplified. The description will focus on the characteristic part.

本例の転がり軸受用潤滑装置の場合、複列円筒ころ軸受３の内輪４を抑え付ける為のナット２４ｂに遠心流惹起部材４２を外嵌支持して、これらナット２４ｂと遠心流惹起部材４２とが、互いに同期して回転する様にしている。この為に本例の場合には、前記ナット２４ｂの外周面の基本形状を円筒状とし、この外周面の円周方向等間隔複数箇所（図示の例では６箇所）に、それぞれが径方向内方に凹入した、係止切り欠き４３、４３を形成している。尚、これら各係止切り欠き４３、４３は、前記ナット２４ｂを車軸２の端部に設けた雄ねじ部２３に螺合し更に締め付ける為の工具の先端部を係止する為の構造を、そのまま利用できる。   In the case of the rolling bearing lubrication device of this example, a centrifugal flow-inducing member 42 is externally supported by a nut 24b for suppressing the inner ring 4 of the double row cylindrical roller bearing 3, and the nut 24b, the centrifugal flow-inducing member 42, However, they rotate in synchronization with each other. For this reason, in the case of this example, the basic shape of the outer peripheral surface of the nut 24b is a cylindrical shape, and each of the outer peripheral surface is radially inward at a plurality of equally spaced locations (six locations in the illustrated example). Locking notches 43, 43 are formed which are recessed in the direction. Each of the locking notches 43 and 43 has a structure for locking the tip of a tool for screwing and further tightening the nut 24b to the male screw 23 provided at the end of the axle 2. Available.

一方、前記遠心流惹起部材４２は、円筒部４４の内周面の円周方向等間隔複数箇所（図示の例では６箇所）に、それぞれが径方向内方に突出した係止突部４５、４５を形成している。前記遠心流惹起部材４２は、これら各係止突部４５、４５と前記各係止切り欠き４３、４３とを係合させつつ、前記円筒部４４を前記ナット２４ｂに外嵌している。この状態で前記遠心流惹起部材４２がこのナット２４ｂの周囲に、このナット２４ｂと同期した回転を自在に支持される。又、この状態で、前記各係止突部４５、４５が、鍔輪９と回り止めリング２５との間に挟持されて、前記遠心流惹起部材４２の軸方向変位が抑えられる。又、この遠心流惹起部材４２は、前記円筒部４４の外周面に遠心流惹起板部４１ｂ、４１ｂを、径方向外方に突出する状態で設けて成る。これら各遠心流惹起板部４１ｂ、４１ｂは、前記ナット２４ｂと共に回転し、軸受箱１の底部に貯溜された潤滑油のうちで前記各遠心流惹起板部４１ｂ、４１ｂの下端部が浸漬された部分の潤滑油に遠心流、即ち、これら各遠心流惹起板部４１ｂ、４１ｂの内径側から外径側に向かう流れを惹起させる。そして、前記複列円筒ころ軸受３の内部の軸方向中央部から前記遠心流惹起部材４２に向かう方向の、潤滑油の流れを惹起させる。   On the other hand, the centrifugal flow-inducing member 42 has locking projections 45 projecting radially inward at a plurality of circumferentially equally spaced locations (six locations in the illustrated example) on the inner circumferential surface of the cylindrical portion 44. 45 is formed. The centrifugal flow inducing member 42 has the cylindrical portion 44 fitted on the nut 24b while engaging the locking protrusions 45 and 45 with the locking notches 43 and 43. In this state, the centrifugal flow inducing member 42 is supported around the nut 24b so as to freely rotate in synchronization with the nut 24b. Further, in this state, the respective locking projections 45, 45 are sandwiched between the saddle wheel 9 and the rotation prevention ring 25, and the axial displacement of the centrifugal flow inducing member 42 is suppressed. The centrifugal flow inducing member 42 is provided with centrifugal flow inducing plate portions 41b and 41b on the outer peripheral surface of the cylindrical portion 44 so as to protrude radially outward. These centrifugal flow-inducing plate portions 41b and 41b rotate together with the nut 24b, and the lower end portions of the centrifugal flow-inducing plate portions 41b and 41b are immersed in the lubricating oil stored in the bottom of the bearing box 1. A centrifugal flow, that is, a flow from the inner diameter side to the outer diameter side of each of the centrifugal flow inducing plate portions 41b and 41b is caused in the lubricating oil of the portion. Then, the flow of the lubricating oil is caused in the direction from the axial central portion inside the double row cylindrical roller bearing 3 toward the centrifugal flow inducing member 42.

上述の様に本例の転がり軸受用潤滑装置は、前述の図８に示した従来構造の第２例の場合と同様に、車軸２の回転に伴って前記遠心流惹起部材４２が、外側列（図１の左側列）の円筒ころ７、７の軸方向外側部分に存在する潤滑油に遠心流を惹起させる事に基づき、外側列の円筒ころ７、７の軸方向内側部分から外側部分に向けて潤滑油の流れを惹起させる。この結果、荷重条件が厳しい、前記外側列の円筒ころ７、７の設置部分に、潤滑油を効率良く循環させられる。   As described above, in the rolling bearing lubrication device of this example, as in the case of the second example of the conventional structure shown in FIG. Based on causing a centrifugal flow to occur in the lubricating oil present in the axially outer portion of the cylindrical rollers 7 and 7 in the left column of FIG. 1, from the axially inner portion to the outer portion of the cylindrical rollers 7 and 7 in the outer row. The flow of lubricating oil is induced. As a result, the lubricating oil can be efficiently circulated through the installed portions of the cylindrical rollers 7 and 7 in the outer row where the load conditions are severe.

特に本例の転がり軸受用潤滑装置の場合には、前記遠心流惹起部材４２を、既存の、即ち、軸受箱１の内側に前記車軸２を回転自在に支持する為に元々必要であった、前記ナット２４ｂの周囲に外嵌支持している為、上述の様に優れた潤滑性能を有する、前記各遠心流惹起板部４１ｂ、４１ｂを備えた構造を、小型且つ軽量に構成できる。即ち、前記遠心流惹起部材４２と前記ナット２４ｂとを径方向に重畳させた状態で設けている為、この遠心流惹起部材４２を設置する事に伴って、鍔輪９や車軸２等、一部の部材の軸方向寸法を大きくする必要がない。この為、前記各遠心流惹起板部４１ｂ、４１ｂを備えた構造を、小型且つ軽量に構成できる。   In particular, in the case of the rolling bearing lubrication device of this example, the centrifugal flow-inducing member 42 was originally necessary for rotatably supporting the axle 2 inside the existing, that is, the inside of the bearing housing 1. Since the outer periphery is supported around the nut 24b, the structure including the centrifugal flow-inducing plate portions 41b and 41b having excellent lubricating performance as described above can be configured to be small and light. That is, since the centrifugal flow inducing member 42 and the nut 24b are provided so as to overlap each other in the radial direction, as the centrifugal flow inducing member 42 is installed, the eaves 9 and the axle 2, etc. There is no need to increase the axial dimension of the member of the part. For this reason, the structure provided with each said centrifugal flow induction board part 41b, 41b can be comprised small and lightweight.

前記遠心流惹起部材４２は、前記鍔輪９とは別体である為、この鍔輪９を構成する硬質金属製である必要がない。前記遠心流惹起部材４２の強度は、回転に伴う遠心力や、潤滑油に浸漬する事に伴って発生する摩擦抵抗に基づく応力、運転に伴って発生する振動等により破損しない程度あれば十分である。従って、前記遠心流惹起部材４２を、軸受鋼の如き硬質金属製とする必要はなく、耐油性を有する合成樹脂や、銅、アルミニウム等の、比較的軟質の金属により造る事ができて、前記各遠心流惹起板部４１ｂ、４１ｂの加工が容易になる。この結果、前記遠心流惹起部材４２の加工コストを抑え、この遠心流惹起部材４２を組み込んだ転がり軸受用潤滑装置の低コスト化を図れる。   Since the centrifugal flow inducing member 42 is separate from the saddle wheel 9, it is not necessary to be made of a hard metal that constitutes the saddle wheel 9. The strength of the centrifugal flow inducing member 42 is sufficient as long as it does not break due to centrifugal force accompanying rotation, stress based on frictional resistance generated when immersed in lubricating oil, vibration generated during operation, and the like. is there. Therefore, the centrifugal flow inducing member 42 need not be made of a hard metal such as bearing steel, but can be made of a relatively soft metal such as oil-resistant synthetic resin, copper, or aluminum. Processing of each centrifugal flow eliciting plate portion 41b, 41b is facilitated. As a result, the processing cost of the centrifugal flow inducing member 42 can be reduced, and the cost of the rolling bearing lubrication device incorporating the centrifugal flow inducing member 42 can be reduced.

本発明を実施する場合に、遠心流惹起部材の外周面形状は、特許文献２に記載された従来構造の第２例の場合と同様、特に問わない。要は、遠心流惹起部材の回転に伴って、この遠心流惹起部材の下端部が浸漬された潤滑油に遠心流を惹起できる形状であれば良い。例えば、図６の（Ａ）〜（Ｆ）に示した様な形状を採用できる。
このうちの（Ａ）に示したものは、円筒部４４の外周面に、外径が異なる３本の遠心流惹起板部を形成したものである。
又、（Ｂ）に示したものは、円筒部４４の外周面に、外径が同じ３本の遠心流惹起板部を形成したものである。
又、（Ｃ）に示したものは、円筒部４４の外周面に、外径が同じ２本の遠心流惹起板部を形成したものである。図１〜５に示した実施の形態の１例には、この（Ｃ）に示した遠心流惹起部材を組み込んでいる。
又、（Ｄ）に示したものは、円筒部４４の外周面に、外径が異なる２本の遠心流惹起板部を形成したものである。
又、（Ｅ）に示したものは、円筒部４４の外周面の遠心流惹起板部を厚肉にし、転がり軸受の開口部に対向する内側面を、外径側に向かうに従って軸方向外側に向かう方向に傾斜した傾斜面としたものである。
更に、（Ｆ）に示したものは、円筒部４４の外周面の遠心流惹起板部を厚肉にし、この遠心流惹起板部の両側面を、中心軸に対し直交する方向の平坦面としたものである。
何れの構造を採用するかは、潤滑油の遠心流惹起能力、強度等、遠心流惹起部材に要求される性能に応じて設計的に定める。 When carrying out the present invention, the shape of the outer peripheral surface of the centrifugal flow inducing member is not particularly limited as in the case of the second example of the conventional structure described in Patent Document 2. In short, any shape may be used as long as the centrifugal flow can be induced in the lubricating oil in which the lower end portion of the centrifugal flow inducing member is immersed in accordance with the rotation of the centrifugal flow inducing member. For example, the shapes as shown in FIGS. 6A to 6F can be adopted.
Among them, the one shown in (A) is one in which three centrifugal flow-inducing plate portions having different outer diameters are formed on the outer peripheral surface of the cylindrical portion 44.
In addition, what is shown in (B) is one in which three centrifugal flow-inducing plate portions having the same outer diameter are formed on the outer peripheral surface of the cylindrical portion 44.
Also, in (C), two centrifugal flow-inducing plate portions having the same outer diameter are formed on the outer peripheral surface of the cylindrical portion 44. The centrifugal flow inducing member shown in (C) is incorporated in one example of the embodiment shown in FIGS.
Further, what is shown in (D) is one in which two centrifugal flow-inducing plate portions having different outer diameters are formed on the outer peripheral surface of the cylindrical portion 44.
Further, in the case shown in (E), the centrifugal flow-inducing plate portion on the outer peripheral surface of the cylindrical portion 44 is thickened, and the inner side surface facing the opening of the rolling bearing is moved outward in the axial direction toward the outer diameter side. The inclined surface is inclined in the direction of heading.
Further, in (F), the centrifugal flow inducing plate portion on the outer peripheral surface of the cylindrical portion 44 is thickened, and both side surfaces of the centrifugal flow inducing plate portion are flat surfaces in a direction perpendicular to the central axis. It is a thing.
Which structure is adopted is determined by design according to the performance required for the centrifugal flow inducing member, such as the centrifugal flow inducing ability and strength of the lubricating oil.

１ 軸受箱
２ 車軸
３、３ａ 複列円筒ころ軸受
４ 内輪
５ 外輪
６ 外輪間座
７ 円筒ころ
８ 内輪本体
９、９ａ 鍔輪
１０ 内輪鍔
１１ 内輪軌道
１２ 外輪軌道
１３ 外輪鍔
１４ 通孔
１５ 保持器
１６ 段部
１７ 前蓋
１８ 円筒部
１９ Ｏリング
２０ 開口部
２１ 油切り
２２ 肩部
２３ 雄ねじ部
２４、２４ａ、２４ｂ ナット
２５ 回り止めリング
２６ 突片
２７ 凹溝
２８ ボルト
２９ ねじ孔
３０ ラビリンスシール
３１ シールリング
３２ 後蓋
３３ Ｏリング
３４ 固定側突条
３５ 回転側突条
３６ スリンガ
３７ 潤滑油溜り
３８ ドレン孔
３９ ねじ蓋
４０ａ、４０ｂ 戻り通路
４１、４１ａ、４１ｂ 遠心流惹起板部
４２ 遠心流惹起部材
４３ 係止切り欠き
４４ 円筒部
４５ 係止突部
４６ 排出孔 DESCRIPTION OF SYMBOLS 1 Bearing case 2 Axle 3, 3a Double row cylindrical roller bearing 4 Inner ring 5 Outer ring 6 Outer ring spacer 7 Cylindrical roller 8 Inner ring main body 9, 9a Eaves ring 10 Inner ring cage 11 Inner ring raceway 12 Outer ring raceway 13 Outer ring cage 14 Through hole 15 Cage 16 Stepped portion 17 Front lid 18 Cylindrical portion 19 O-ring 20 Opening portion 21 Oil drain 22 Shoulder portion 23 Male screw portion 24, 24a, 24b Nut 25 Non-rotating ring 26 Projection piece 27 Concave groove 28 Bolt 29 Screw hole 30 Labyrinth seal 31 Seal Ring 32 Rear lid 33 O-ring 34 Fixed-side ridge 35 Rotating-side ridge 36 Slinger 37 Lubricating oil reservoir 38 Drain hole 39 Screw lid 40a, 40b Return passage 41, 41a, 41b Centrifugal flow plate member 42 Centrifugal flow member 43 Locking notch 44 Cylindrical part 45 Locking protrusion 46 Discharge hole

Claims (2)

回転しないハウジングの内径側に回転軸を支持する為の転がり軸受の内部に潤滑油を循環させる為、前記ハウジングの下端部内側に設けられた潤滑油溜りと、前記転がり軸受を構成する複数個の転動体の列を挟んで、当該列の軸方向片側に設けられた、外径側を前記潤滑油溜りに貯溜された潤滑油内に開口させると共に、内径側を前記転がり軸受の内部に通じさせた給油通路と、前記回転軸と共に回転する状態で前記各転動体の列を挟んで軸方向他側に設けられ、下部外径寄り部分を前記潤滑油溜りに貯溜された潤滑油中に浸漬させた、円環状の遠心流惹起部材と、この遠心流惹起部材と前記潤滑油溜りとの間に設けられた戻り通路とを備えた転がり軸受用潤滑装置に於いて、前記遠心流惹起部材が、前記転がり軸受を構成する内輪の軸方向他側に隣接する状態で設けられて前記回転軸と共に回転する円環状部材に、この円環状部材と共に回転する状態で外嵌支持されている事を特徴とする転がり軸受用潤滑装置。   In order to circulate the lubricating oil inside the rolling bearing for supporting the rotating shaft on the inner diameter side of the non-rotating housing, a lubricating oil reservoir provided inside the lower end portion of the housing and a plurality of rollers constituting the rolling bearing The outer diameter side provided on one side in the axial direction of the row of rolling elements is opened in the lubricating oil stored in the lubricating oil reservoir, and the inner diameter side is communicated with the inside of the rolling bearing. The oil supply passage and the row of the rolling elements in a state of rotating together with the rotating shaft are provided on the other side in the axial direction, and the lower outer diameter portion is immersed in the lubricating oil stored in the lubricating oil reservoir. Further, in a rolling bearing lubrication device comprising an annular centrifugal flow inducing member and a return passage provided between the centrifugal flow inducing member and the lubricating oil reservoir, the centrifugal flow inducing member comprises: Axial direction of inner ring constituting the rolling bearing An annular member which rotates together with the rotary shaft is provided in a state adjacent to the side, the rolling bearing lubrication device, characterized in that is fitted supported in a state of rotating together with the annular member. 回転軸が鉄道車両用の車軸であり、ハウジングが軸受箱であり、転がり軸受が、外周面に複列円筒状の内輪軌道を有する内輪と、それぞれの内周面に円筒状の外輪軌道を有する１対の外輪と、これら両外輪同士の間に挟持された外輪間座と、前記両内輪軌道と前記両外輪軌道との間に、両列毎に複数個ずつ転動自在に設けられた、それぞれが転動体である円筒ころとを備えたものであり、給油通路が、前記外輪間座の一部を径方向に貫通する状態で設けられた通孔であり、環状部材が前記車軸に対して前記内輪を固定する為のナットであり、このナットに遠心流惹起部材を外嵌した状態で、これらナットの外周面と遠心流惹起部材の内周面とを非円形係合させている、請求項１に記載した転がり軸受用潤滑装置。   The rotating shaft is an axle for a railway vehicle, the housing is a bearing box, and the rolling bearing has an inner ring having a double-row cylindrical inner ring raceway on the outer peripheral surface and a cylindrical outer ring raceway on each inner peripheral surface. Between the pair of outer rings, the outer ring spacer sandwiched between the two outer rings, and the inner ring raceways and the outer ring raceways, a plurality of rows are provided for each row so as to freely roll. Each of which is provided with a cylindrical roller that is a rolling element, the oil supply passage is a through hole provided in a state of passing through a part of the outer ring spacer in the radial direction, and the annular member with respect to the axle A nut for fixing the inner ring, and the outer peripheral surface of the nut and the inner peripheral surface of the centrifugal flow inducing member are non-circularly engaged in a state in which the centrifugal flow inducing member is externally fitted to the nut. The rolling bearing lubrication device according to claim 1.

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