JP4519060B2 - Double row tapered roller bearing - Google Patents

Double row tapered roller bearing Download PDF

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Publication number
JP4519060B2
JP4519060B2 JP2005329014A JP2005329014A JP4519060B2 JP 4519060 B2 JP4519060 B2 JP 4519060B2 JP 2005329014 A JP2005329014 A JP 2005329014A JP 2005329014 A JP2005329014 A JP 2005329014A JP 4519060 B2 JP4519060 B2 JP 4519060B2
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tapered roller
double
roller bearing
row
outer ring
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JP2007132496A (en
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達也 大本
洋右 大矢
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NTN Corp
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NTN Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/52—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers
    • F16C33/523—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers with pins extending into holes or bores on the axis of the rollers
    • F16C33/526—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers with pins extending into holes or bores on the axis of the rollers extending through the rollers and joining two lateral cage parts
    • 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
    • F16C19/383—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • 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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements

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

Description

この発明は、風力発電機の主軸等、低速回転、高負荷環境下で使用される複列円錐ころ軸受に関するものである。   The present invention relates to a double row tapered roller bearing used in a low speed rotation and high load environment such as a main shaft of a wind power generator.

従来、風力発電機の主軸等、低速回転で大きなラジアル荷重およびアキシアル荷重の両方が負荷される環境で使用される複列円錐ころ軸受が、例えば、特開２００３−４９８４３号公報（特許文献１）に記載されている。   Conventionally, a double-row tapered roller bearing used in an environment where both a large radial load and an axial load are applied at a low speed such as a main shaft of a wind power generator is disclosed in, for example, Japanese Patent Application Laid-Open No. 2003-49843 (Patent Document 1). It is described in.

同公報に記載されている複列円錐ころ軸受１は、図７に示すように、間座２ａを挟んで２つの内輪部材の小径側端部を突き合わせた内輪２と、中央部に径方向に貫通する給油口３ａを有する外輪３と、内輪２および外輪３の間に複列に配置された円錐ころ４と、円錐ころ４の間隔を保持するピン型保持器５とを備える。   As shown in FIG. 7, the double-row tapered roller bearing 1 described in the publication has an inner ring 2 in which the small-diameter side ends of the two inner ring members are abutted across a spacer 2a, and a radial direction at the center. An outer ring 3 having a penetrating oil supply port 3 a, a tapered roller 4 arranged in a double row between the inner ring 2 and the outer ring 3, and a pin type cage 5 that holds the interval between the tapered rollers 4 are provided.

また、円錐ころ４は、小端面から大端面に貫通する貫通孔４ａを有し、ピン型保持器５は、貫通孔４ａに挿通するピン５ａと、ピン５ａの両端に円錐ころ４の両端面に当接するリング状の一対の側板５ｂとを有する。
特開２００３−４９８４３号公報 The tapered roller 4 has a through hole 4a penetrating from the small end surface to the large end surface. The pin type cage 5 has a pin 5a inserted into the through hole 4a and both end surfaces of the tapered roller 4 at both ends of the pin 5a. And a pair of ring-shaped side plates 5b that come into contact with each other.
JP 2003-49843 A

上記構成のような複列円錐ころ軸受１において、例えば、風力発電機の主軸のように水平方向に延びる回転軸を支持する場合には、給油口３ａから供給される潤滑油の大部分は間座２ａに沿って軸受下部に流れ、円錐ころ４の転動面と内輪２および外輪３の軌道面に直接供給される潤滑油量は少ない。したがって、供給される潤滑油量が少ないと、潤滑不良による焼付きが懸念される。   In the double-row tapered roller bearing 1 having the above-described configuration, for example, when supporting a rotating shaft extending in the horizontal direction like the main shaft of a wind power generator, most of the lubricating oil supplied from the oil supply port 3a is in between. The amount of lubricating oil that flows along the seat 2a to the lower part of the bearing and is directly supplied to the rolling surfaces of the tapered rollers 4 and the raceways of the inner ring 2 and the outer ring 3 is small. Therefore, if the amount of lubricating oil supplied is small, there is a concern about seizure due to poor lubrication.

また、給油口３ａから供給される潤滑油の流路としては、例えば、側板５ｂと円錐ころ４との当接面から内輪軌道面に至る経路や、側板５ｂと円錐ころ４との当接面から貫通孔４ａを経由して内輪大鍔面に至る経路等が考えられる。しかし、円錐ころ４の両端に配置された側板５ｂが当接面への潤滑油の流入を阻害するため、軸受各部に潤滑油が供給されにくい構造となっている。   Moreover, as a flow path of the lubricating oil supplied from the oil supply port 3a, for example, a path from the contact surface between the side plate 5b and the tapered roller 4 to the inner ring raceway surface, or the contact surface between the side plate 5b and the tapered roller 4 is used. A route from the through hole 4a to the inner ring large collar surface is conceivable. However, since the side plates 5b arranged at both ends of the tapered roller 4 inhibit the inflow of the lubricating oil to the contact surface, the lubricating oil is difficult to be supplied to each part of the bearing.

特に、風力発電機の主軸等の低速回転下で使用する場合には、軸受回転時の遠心力による潤滑油の供給も少ない。また、高負荷環境下では潤滑油の供給不足による軌道面の焼付き等のトラブルの危険性も高い。   In particular, when used under a low-speed rotation of the main shaft of a wind power generator, etc., there is little supply of lubricating oil due to the centrifugal force during bearing rotation. In addition, in a high load environment, there is a high risk of troubles such as seizure of the raceway surface due to insufficient supply of lubricating oil.

そこで、この発明の目的は、軸受各部に十分な量の潤滑油を供給可能な構造とすることにより、潤滑性能に優れた複列円錐ころ軸受を提供することである。   Accordingly, an object of the present invention is to provide a double-row tapered roller bearing having excellent lubricating performance by providing a structure capable of supplying a sufficient amount of lubricating oil to each part of the bearing.

この発明に係る複列円錐ころ軸受は、内輪と、外径面から内径面に貫通する給油口を有する外輪と、内輪および外輪の間に複列に配置される複数の円錐ころとを備える。そして、給油口の内径面側開口部は複数あり、それらは外輪に配置された複列の軌道面間の軸方向中央部から左右にずれた位置に設けられる。   The double-row tapered roller bearing according to the present invention includes an inner ring, an outer ring having an oil supply port penetrating from the outer diameter surface to the inner diameter surface, and a plurality of tapered rollers arranged in a double row between the inner ring and the outer ring. There are a plurality of openings on the inner diameter surface side of the fuel filler opening, and they are provided at positions shifted left and right from the central portion in the axial direction between the double-row raceway surfaces arranged in the outer ring.

上記構成とすることにより、給油口から軌道面に直接供給される潤滑油量が増加する。これにより、複列円錐ころ軸受の潤滑性能が向上し、潤滑不良による焼付きを防止することができる。また、潤滑効率が向上するので、従来の潤滑状態を維持する場合には、供給する潤滑油量を少なくすることが可能となる。   By setting it as the said structure, the amount of lubricating oil supplied directly to a track surface from an oil filler opening increases. Thereby, the lubrication performance of the double row tapered roller bearing is improved, and seizure due to poor lubrication can be prevented. Further, since the lubrication efficiency is improved, the amount of lubricating oil to be supplied can be reduced when the conventional lubrication state is maintained.

好ましくは、外輪は複数の前記給油口を有し、外輪に配置された複列の軌道面間の軸方向中央部より右側に配置される給油口と、左側に配置される給油口とは、円周方向にずれた位置に配置される。これにより、各列の軌道面に均等に潤滑油を供給することが可能となると共に、外輪の強度の低下を抑えることができる。   Preferably, the outer ring has a plurality of the oil supply ports, and the oil supply port arranged on the right side from the central portion in the axial direction between the double-row raceway surfaces arranged in the outer ring and the oil supply port arranged on the left side are: It is arranged at a position shifted in the circumferential direction. As a result, it is possible to evenly supply the lubricating oil to the raceway surfaces of each row and to suppress a decrease in strength of the outer ring.

好ましくは、円錐ころは小端面から大端面に貫通する貫通孔を有し、複列円錐ころ軸受は、貫通孔に挿通するピンと、このピンの両端に円錐ころの両端面に当接するリング形状の一対の側板とを有するピン型保持器をさらに備える。そして、軸受中央部側の側板の外径面は、円錐ころの端面に対して鋭角をなす傾斜面である。これにより、傾斜面上の潤滑油が、側板と円錐ころの端面との間に流入しやすくなるので、複列円錐ころ軸受の潤滑性能がさらに向上する。   Preferably, the tapered roller has a through-hole penetrating from the small end surface to the large end surface, and the double-row tapered roller bearing has a pin that is inserted into the through-hole, and a ring shape that abuts both end surfaces of the tapered roller at both ends of the pin. A pin type cage having a pair of side plates is further provided. The outer diameter surface of the side plate on the bearing center side is an inclined surface that forms an acute angle with the end surface of the tapered roller. As a result, the lubricating oil on the inclined surface easily flows between the side plate and the end surface of the tapered roller, so that the lubricating performance of the double row tapered roller bearing is further improved.

この発明は、給油口から軌道面に直接供給される潤滑油量を増加することにより、潤滑性能に優れた複列円錐ころ軸受を得ることができる。   According to the present invention, it is possible to obtain a double-row tapered roller bearing with excellent lubricating performance by increasing the amount of lubricating oil directly supplied from the oil supply port to the raceway surface.

図１〜図５を参照して、この発明の一実施形態に係る複列円錐ころ軸受１１を説明する。   With reference to FIGS. 1-5, the double row tapered roller bearing 11 which concerns on one Embodiment of this invention is demonstrated.

複列円錐ころ軸受１１は、図１に示すように、間座１２ａを挟んで２つの内輪部材の小径側端部を突き合わせた内輪１２と、外径面から内径面に貫通した複数の給油口１３ａ，１３ｂを有する外輪１３と、内輪１２および外輪１３の間に複列に配置され、小端面から大端面に貫通する貫通孔１４ａを有する複数の円錐ころ１４と、円錐ころ１４の間隔を保持するピン型保持器１５とを備える。   As shown in FIG. 1, the double-row tapered roller bearing 11 includes an inner ring 12 in which the end portions on the small diameter side of two inner ring members are abutted with a spacer 12a interposed therebetween, and a plurality of oil supply ports penetrating from the outer diameter surface to the inner diameter surface. An outer ring 13 having 13a and 13b, a plurality of tapered rollers 14 arranged in a double row between the inner ring 12 and the outer ring 13 and having through holes 14a penetrating from the small end surface to the large end surface, and the interval between the tapered rollers 14 are maintained. The pin type holder 15 is provided.

給油口１３ａ，１３ｂは、外輪１３に配置された複列の軌道面間の軸方向中央部から左右にずれた位置、図１に示す複列円錐ころ軸受１１では、側板１５ｂの真上に配置される。また、図２に示すように、外輪１３に配置された複列の軌道面間の軸方向中央部より右側に配置される給油口１３ａと、左側に配置される給油口１３ｂとは、円周方向にずれた位置に配置される。   The oil filler ports 13a and 13b are arranged at positions shifted left and right from the axial center between the double-row raceway surfaces arranged in the outer ring 13, in the double-row tapered roller bearing 11 shown in FIG. 1, just above the side plate 15b. Is done. Further, as shown in FIG. 2, the fuel filler port 13 a disposed on the right side from the central portion in the axial direction between the double-row raceway surfaces disposed on the outer ring 13 and the fuel filler port 13 b disposed on the left side are circumferential. It is arranged at a position shifted in the direction.

ピン型保持器１５は、図３（ａ）および（ｂ）に示すように、貫通孔１４ａに挿通するピン１５ａと、ピン１５ａの両端に円錐ころ１４の両端面に当接するリング形状の一対の側板１５ｂとを有し、一対の側板１５ｂのうち、軸受中央部側の外径面は、円錐ころ１４の端面に対して鋭角をなす傾斜面１５ｃである。さらに、図４に示すように、円錐ころ１４の端面に当接する側板１５ｂの当接面と、側板１５ｂの傾斜面１５ｃとの角部には、面取り部１５ｄが設けられている。   As shown in FIGS. 3A and 3B, the pin-type cage 15 includes a pin 15a inserted into the through hole 14a and a pair of ring-shaped abutting ends of the tapered roller 14 at both ends of the pin 15a. Of the pair of side plates 15 b, the outer diameter surface on the bearing central portion side is an inclined surface 15 c that forms an acute angle with respect to the end surface of the tapered roller 14. Further, as shown in FIG. 4, chamfered portions 15d are provided at corners of the contact surface of the side plate 15b that contacts the end surface of the tapered roller 14 and the inclined surface 15c of the side plate 15b.

上記構成とすることにより、給油口１３ａから側板１５ｂの傾斜面１５ｃに直接供給される潤滑油量が増加する。そして、側板１５ｂの外径面を傾斜面とすることにより、潤滑油が傾斜面１５ｃに沿って円錐ころ１４との当接面に流入しやすくなる。また、面取り部１５ｄを設けることによって、側板１５ｂと円錐ころ１４との当接面への流入路の入口が広がるので、傾斜面１５ｃに沿って流入する潤滑油の流れを妨げることがなくなる。   By setting it as the said structure, the amount of lubricating oil supplied directly from the oil supply port 13a to the inclined surface 15c of the side plate 15b increases. And by making the outer-diameter surface of the side plate 15b into an inclined surface, it becomes easy for lubricating oil to flow into the contact surface with the tapered roller 14 along the inclined surface 15c. Further, by providing the chamfered portion 15d, the inlet of the inflow path to the contact surface between the side plate 15b and the tapered roller 14 is widened, so that the flow of the lubricating oil flowing along the inclined surface 15c is not hindered.

当接面に流入した潤滑油は、図５に示すように、内輪軌道面全域および貫通孔１４ａに供給されることとなる。また、貫通孔１４ａ内部に流入した潤滑油は、円錐ころ１４の自転および公転による遠心力で貫通孔１４ａの大端面側に、さらには、円錐ころ１４の大端面と内輪１２の大鍔面との当接部分等にも移動する。なお、図５中の太線は潤滑油の流れを示す。したがって、側板１５ｂと円錐ころ１４との当接面への潤滑油の供給量が増加することにより、軸受各部にも潤滑油を十分に供給することが可能となる。   As shown in FIG. 5, the lubricating oil flowing into the contact surface is supplied to the entire inner ring raceway surface and the through hole 14a. Further, the lubricating oil that has flowed into the through hole 14 a is caused by centrifugal force due to the rotation and revolution of the tapered roller 14 to the large end surface side of the through hole 14 a, and further, the large end surface of the tapered roller 14 and the large collar surface of the inner ring 12. It also moves to the abutting part. In addition, the thick line in FIG. 5 shows the flow of lubricating oil. Accordingly, the amount of lubricating oil supplied to the contact surface between the side plate 15b and the tapered roller 14 is increased, so that it is possible to sufficiently supply the lubricating oil to each part of the bearing.

上記構成の複列円錐ころ軸受１１は、従来と比較して潤滑性能が向上するので、潤滑油の供給不足による焼付き等のトラブルを回避することができる。また、潤滑効率も向上するので、従来の潤滑状態を維持する場合には、潤滑油の供給量を減らすことが可能となる。   The double-row tapered roller bearing 11 having the above-described configuration has improved lubrication performance as compared with the conventional one, so that troubles such as seizure due to insufficient supply of lubricating oil can be avoided. Also, since the lubrication efficiency is improved, the supply amount of the lubricating oil can be reduced when the conventional lubrication state is maintained.

次に、図６を参照して、この発明の他の実施形態に係る複列円錐ころ軸受２１を説明する。   Next, a double-row tapered roller bearing 21 according to another embodiment of the present invention will be described with reference to FIG.

複列円錐ころ軸受２１は、図１に示したような複列円錐ころ軸受１１と同様に、内輪２２と、外輪２３と、円錐ころ２４と、ピン型保持器２５とを備える。また、外輪２３に複数設けられた給油口２３ａは、それぞれ外径面側開口端は中央に１箇所で、内部で枝分かれして内径面側開口端は外輪２３に配置された複列の軌道面間の軸方向中央部から左右にずれた２箇所に設けられている。   The double row tapered roller bearing 21 includes an inner ring 22, an outer ring 23, a tapered roller 24, and a pin type retainer 25, similarly to the double row tapered roller bearing 11 as shown in FIG. 1. In addition, a plurality of oil supply ports 23 a provided in the outer ring 23 each have an outer diameter surface side opening end at one central position, branching inside, and an inner diameter surface side opening end disposed in the outer ring 23. It is provided in two places shifted left and right from the central portion in the axial direction.

上記構成とすることにより、図１に示した実施形態の効果に加えて、従来の給油装置をそのまま利用することができるので、設計変更等を伴わずに軸受の交換をすることが可能となる。   By adopting the above configuration, in addition to the effect of the embodiment shown in FIG. 1, the conventional oiling device can be used as it is, so that it is possible to replace the bearing without design change or the like. .

また、ピン型保持器２５は、基本構成はピン型保持器１５と同様であって、傾斜面２５ｃ上の円錐ころ１４の端面から離れた位置に、径方向に突出する凸部２５ｄを有する。図６に示す実施形態においては、傾斜面２５ｃ上の円錐ころ２４から最も離れた位置に凸部２５ｄを設けている。   The pin type retainer 25 has a basic configuration similar to that of the pin type retainer 15, and has a convex portion 25 d protruding in the radial direction at a position away from the end surface of the tapered roller 14 on the inclined surface 25 c. In the embodiment shown in FIG. 6, the convex portion 25d is provided at a position farthest from the tapered roller 24 on the inclined surface 25c.

上記構成とすることにより、図１に示した実施形態の効果に加えて、傾斜面２５ｃ上の潤滑油が流出するのを抑制することができるので、より多くの潤滑油を側板２５ｂと円錐ころ２４との当接面に供給することが可能となる。   With the above configuration, in addition to the effect of the embodiment shown in FIG. 1, it is possible to prevent the lubricating oil on the inclined surface 25c from flowing out, so that more lubricating oil is supplied to the side plate 25b and the tapered roller. It becomes possible to supply to the contact surface with 24.

なお、上記の各実施形態において、給油口１３ａ，２３ａは外輪１３，２３上に１箇所であってもよいし、複数箇所設けてもよい。   In each of the above-described embodiments, the oil filler ports 13a and 23a may be provided on the outer rings 13 and 23 at a single location or a plurality of locations.

また、上記の各実施形態の複列円錐ころ軸受は、円錐ころの小径側端部を突き合わせた背面組み合わせ軸受であって、円錐ころの小端面に当接する側板の外径面を傾斜面とした例を示した。背面組み合わせとした場合には、軸受の回転中心線と、左右の列の円錐ころと内外輪の接触線との交点の距離（以下「作用点間距離」という）が長くなるので、ラジアル剛性が向上する。   Further, the double row tapered roller bearing of each of the above embodiments is a back combination bearing in which the small-diameter end of the tapered roller is abutted, and the outer diameter surface of the side plate contacting the small end surface of the tapered roller is an inclined surface. An example is shown. In the case of the rear combination, the distance between the center of rotation of the bearing and the contact line between the tapered rollers in the left and right rows and the inner and outer rings (hereinafter referred to as the “distance between the operating points”) is increased, so that the radial rigidity is increased. improves.

一方、円錐ころの大径側端部を突き合わせた正面組み合わせ軸受であって、円錐ころの大端面に当接する側板の外径面を傾斜面としてもよい。正面組み合わせとした場合には、外輪の肉厚が円周上であまり差のないバランスの良い設計ができるとともに、同じ断面高さであれば、背面組み合わせ軸受より負荷容量を大きくすることができる。   On the other hand, in the front combination bearing in which the large-diameter end of the tapered roller is abutted, the outer diameter surface of the side plate contacting the large end surface of the tapered roller may be an inclined surface. In the case of the front combination, a well-balanced design in which the thickness of the outer ring is not much different on the circumference can be achieved, and the load capacity can be made larger than that of the rear combination bearing if the cross-sectional height is the same.

また、上記の各実施形態においては、側板の外径面にのみ上記の加工を施す例を示したが、これに限ることなく、側板の内径面にのみ上記加工を施してもよいし、外径面および内径面の両方に上記加工を施してもよい。   Further, in each of the above embodiments, the example in which the above processing is performed only on the outer diameter surface of the side plate has been described. However, the present invention is not limited thereto, and the above processing may be performed only on the inner diameter surface of the side plate. You may give the said process to both a radial surface and an internal diameter surface.

さらに、上記実施形態においては、ピン型保持器を備える複列円錐ころ軸受の例を示したが、これに限ることなく、この発明は、鋼板をプレス加工して製造した保持器を有する複列円錐ころ軸受にも適用することができる。   Furthermore, in the said embodiment, although the example of the double row tapered roller bearing provided with a pin-type cage was shown, this invention is not limited to this, This invention is a double row which has the cage manufactured by pressing a steel plate. It can also be applied to a tapered roller bearing.

以上、図面を参照してこの発明の実施形態を説明したが、この発明は、図示した実施形態のものに限定されない。図示した実施形態に対して、この発明と同一の範囲内において、あるいは均等の範囲内において、種々の修正や変形を加えることが可能である。   As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

この発明は、低速回転、高負荷環境下で使用される複列円錐ころ軸受に有利に利用される。   The present invention is advantageously used for a double row tapered roller bearing used in a low speed rotation and high load environment.

この発明の一実施形態に係る複列円錐ころ軸受を示す図である。It is a figure which shows the double row tapered roller bearing which concerns on one Embodiment of this invention. 図１に使用する外輪外径面の部分拡大図である。It is the elements on larger scale of the outer ring | wheel outer diameter surface used for FIG. 図１に示したピン型保持器であって、（ａ）が正面図、（ｂ）が側面図である。It is a pin type holder shown in Drawing 1, and (a) is a front view and (b) is a side view. 図２に示したピン型保持器の側板外径面周辺の拡大図である。FIG. 3 is an enlarged view of the periphery of a side plate outer diameter surface of the pin type cage shown in FIG. 2. 図２に示した複列円錐ころ軸受の潤滑油の流れを示す図である。It is a figure which shows the flow of the lubricating oil of the double row tapered roller bearing shown in FIG. この発明の他の実施形態に係る複列円錐ころ軸受を示す図である。It is a figure which shows the double row tapered roller bearing which concerns on other embodiment of this invention. 従来の複列円錐ころ軸受を示す図である。It is a figure which shows the conventional double row tapered roller bearing.

符号の説明Explanation of symbols

１，１１，２１ 複列円錐ころ軸受、２，１２，２２ 内輪、２ａ，１２ａ，２２ａ 間座、３，１３，２３ 外輪、３ａ，１３ａ，１３ｂ，２３ａ 給油口、４，１４，２４ 円錐ころ、４ａ，１４ａ，２４ａ 貫通孔、５，１５，２５ ピン型保持器、５ａ，１５ａ，２５ａ ピン、５ｂ，１５ｂ，２５ｂ 側板、１５ｃ，２５ｃ 傾斜面、２５ｄ 凸部、１５ｄ 面取り部。
1,11,21 Double row tapered roller bearing, 2,12,22 Inner ring, 2a, 12a, 22a spacer, 3,13,23 Outer ring, 3a, 13a, 13b, 23a Oil supply port, 4,14,24 Conical roller 4a, 14a, 24a Through hole, 5, 15, 25 pin type cage, 5a, 15a, 25a pin, 5b, 15b, 25b side plate, 15c, 25c inclined surface, 25d convex portion, 15d chamfered portion.

Claims (5)

内輪と、
外径面から内径面に貫通する給油口を有する外輪と、
前記内輪および前記外輪の間に複列に配置され、小端面から大端面に貫通する貫通孔を有する複数の円錐ころと、
前記貫通孔に挿通するピンと、このピンの両端に前記円錐ころの両端面に当接するリング形状の一対の側板とを有するピン型保持器とを備え、
前記給油口の内径面側開口部は複数あり、それらは前記外輪に配置された複列の軌道面間の軸方向中央部から左右にずれた位置に設けられており、
前記複数の給油口の内径面側開口部は、前記側板と対向して設けられ、
軸受中央部側の前記側板の外径面は、前記円錐ころの端面に対して鋭角をなす傾斜面である、複列円錐ころ軸受。 Inner ring,
An outer ring having an oil filler port penetrating from the outer diameter surface to the inner diameter surface;
A plurality of tapered rollers disposed in a double row between the inner ring and the outer ring and having a through-hole penetrating from the small end surface to the large end surface ;
A pin type cage having a pin inserted into the through hole, and a pair of ring-shaped side plates contacting both end surfaces of the tapered roller at both ends of the pin ;
There are a plurality of openings on the inner diameter surface side of the fuel filler port, and they are provided at positions shifted to the left and right from the central portion in the axial direction between the double-row track surfaces arranged in the outer ring,
The inner diameter surface side openings of the plurality of oil filler ports are provided to face the side plate,
The double-row tapered roller bearing , wherein an outer diameter surface of the side plate on the bearing central portion side is an inclined surface that forms an acute angle with respect to an end surface of the tapered roller. 前記傾斜面は、面取りを除いて、前記側板の外径面全体が傾斜した形状である、請求項１に記載の複列円錐ころ軸受。  The double-row tapered roller bearing according to claim 1, wherein the inclined surface has a shape in which an entire outer diameter surface of the side plate is inclined except for chamfering. 前記傾斜面には、前記円錐ころの端面から離れた位置に、径方向に突出する凸部が設けられている、請求項１に記載の複列円錐ころ軸受。  The double-row tapered roller bearing according to claim 1, wherein the inclined surface is provided with a convex portion protruding in a radial direction at a position away from an end surface of the tapered roller. 前記給油口は、径方向に真っ直ぐに延びる形状である、請求項１〜３のいずれかに記載の複列円錐ころ軸受。  The double-row tapered roller bearing according to any one of claims 1 to 3, wherein the oil filler port has a shape extending straight in a radial direction. 前記外輪は、複数の前記給油口を有し、
前記外輪に配置された複列の軌道面間の軸方向中央部より右側に配置される前記給油口と、左側に配置される前記給油口とは、円周方向にずれた位置に配置される、請求項１〜４のいずれかに記載の複列円錐ころ軸受。 The outer ring has a plurality of the fuel filler openings,
The oil supply port arranged on the right side of the axial center between the double-row raceway surfaces arranged on the outer ring and the oil supply port arranged on the left side are arranged at positions shifted in the circumferential direction. The double-row tapered roller bearing according to any one of claims 1 to 4 .
JP2005329014A 2005-11-14 2005-11-14 Double row tapered roller bearing Expired - Fee Related JP4519060B2 (en)

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CN103807292A (en) * 2012-11-06 2014-05-21 优必胜(上海)精密轴承制造有限公司 Reinforced type tapered roller bearing
CN113154017B (en) * 2021-04-07 2022-11-08 浙江兆丰机电股份有限公司 Oil slinger for lubricating main bevel gear bearing and main bevel gear bearing thereof

Citations (7)

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Publication number Priority date Publication date Assignee Title
JPS57124618U (en) * 1981-01-28 1982-08-03
JPS58189818U (en) * 1982-06-11 1983-12-16 日本精工株式会社 Lubricating device for outer ring rotating bearing
JPS63180726U (en) * 1987-05-14 1988-11-22
JPH0616721U (en) * 1992-02-24 1994-03-04 秀一 永野 bearing
JP2001165173A (en) * 1999-12-07 2001-06-19 Nsk Ltd Roller bearing
JP2003049843A (en) * 2001-08-06 2003-02-21 Nsk Ltd Roller bearing
JP2005221001A (en) * 2004-02-05 2005-08-18 Nsk Ltd Tapered roller bearing

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57124618U (en) * 1981-01-28 1982-08-03
JPS58189818U (en) * 1982-06-11 1983-12-16 日本精工株式会社 Lubricating device for outer ring rotating bearing
JPS63180726U (en) * 1987-05-14 1988-11-22
JPH0616721U (en) * 1992-02-24 1994-03-04 秀一 永野 bearing
JP2001165173A (en) * 1999-12-07 2001-06-19 Nsk Ltd Roller bearing
JP2003049843A (en) * 2001-08-06 2003-02-21 Nsk Ltd Roller bearing
JP2005221001A (en) * 2004-02-05 2005-08-18 Nsk Ltd Tapered roller bearing

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