JP2008002659A - High-speed rotation single row cylindrical roller bearing - Google Patents

High-speed rotation single row cylindrical roller bearing Download PDF

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Publication number
JP2008002659A
JP2008002659A JP2006175370A JP2006175370A JP2008002659A JP 2008002659 A JP2008002659 A JP 2008002659A JP 2006175370 A JP2006175370 A JP 2006175370A JP 2006175370 A JP2006175370 A JP 2006175370A JP 2008002659 A JP2008002659 A JP 2008002659A
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Prior art keywords
cage
bearing
cylindrical roller
width
inner ring
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JP2006175370A
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Japanese (ja)
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Naota Yamamoto
直太 山本
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2006175370A priority Critical patent/JP2008002659A/en
Publication of JP2008002659A publication Critical patent/JP2008002659A/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
    • 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
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • 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
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—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
    • F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner 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
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row of rollers

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a single row cylindrical roller bearing with a cage of an inner ring guide type, having stable high-speed operation while reducing a lubricant to flow from a gap between an inner ring and an annular portion of the cage to the outside of the bearing. <P>SOLUTION: The high-speed rotation single row cylindrical roller bearing comprises the annular portion 11 whose inner diameter face is composed of a sectionally tapered portion 11a having a larger diameter at the axial center and a cylindrical guide face 11b opposed to the cage guide face of the inner ring 1 at the axial outside beyond the tapered portion 11a. The bearing adopts such a constitution that a ratio Lw/B of the roller length Lw (mm) of a cylindrical roller 4 to a bearing width B is 0.3≤Lw/B<0.4, the width L (mm) of the annular portion 11 is (B-Lw-1)/2, a width L1 (mm) of the cylindrical guide face 11b is L1≥L×0.2, and an inclination θ (degree) of the tapered portion 11a to the cylindrical guide face 11b is θ≤10. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

この発明は、かご形保持器を備えた単列円筒ころ軸受に関し、特に工作機械、ジェットエンジン、ガスタービン等に設けられた高速回転軸を支持するのに好適なものに関する。   The present invention relates to a single-row cylindrical roller bearing provided with a cage retainer, and more particularly to a bearing suitable for supporting a high-speed rotating shaft provided in a machine tool, a jet engine, a gas turbine or the like.

例えば、マシニングセンタ、ＣＮＣ旋盤、フライス盤等の工作機械の主軸装置は、ワークの加工効率や精度を高める等の理由から高速回転で運転される場合が多く、特に最近は主軸回転速度のより高速化の傾向が顕著である。   For example, spindle devices of machine tools such as machining centers, CNC lathes, and milling machines are often operated at a high speed for reasons such as improving the machining efficiency and accuracy of workpieces. The trend is remarkable.

一般に、工作機械の主軸装置において、主軸は、フロント側（工具側）及びリア側（反工具側）にそれぞれ配置された転がり軸受でハウジングに対して回転自在に支持される。   In general, in a spindle device of a machine tool, the spindle is rotatably supported with respect to a housing by rolling bearings arranged on a front side (tool side) and a rear side (counter tool side).

主軸装置のリア側には、単列円筒ころ軸受が多用されている。これは、主軸の軸方向変位を円筒ころと軌道面との間のスライド変位で吸収し又は逃がすことができ、また、円筒ころ軸受のラジアル荷重の負荷能力が玉軸受よりも高く、主軸剛性を確保する上でも有利だからである。   Single row cylindrical roller bearings are frequently used on the rear side of the main shaft device. This is because the axial displacement of the main shaft can be absorbed or released by the slide displacement between the cylindrical roller and the raceway surface, and the load capacity of the radial load of the cylindrical roller bearing is higher than that of the ball bearing, and the rigidity of the main shaft is increased. This is because it is advantageous for securing.

従来から、特に高速回転する軸を内輪案内方式の単列円筒ころ軸受で支持する場合には、アンダーレース潤滑方式が採用されている。ここで、アンダーレース潤滑方式とは、内輪の内径面から外径面まで貫通する油穴を通して遠心力により軸受内部に潤滑油を供給する潤滑方式のことである。このアンダーレース潤滑方式では、遠心力によって内輪の内径面から外径面まで貫通する油穴で潤滑剤を供給するため、Ｄｍｎ＝100万以上の高速回転する軸受内に比較的効率よく潤滑剤を供給することができる（例えば、特許文献１）。
ここで、Ｄｍｎは、転動体ＰＣＤ〔ｍｍ〕×回転数〔ｍｉｎ−１〕により算出される。 Conventionally, an under-race lubrication method has been adopted particularly when a high-speed rotating shaft is supported by an inner ring guide type single-row cylindrical roller bearing. Here, the under-lace lubrication method is a lubrication method in which lubricating oil is supplied into the bearing by centrifugal force through an oil hole penetrating from the inner diameter surface to the outer diameter surface of the inner ring. In this under-race lubrication system, the lubricant is supplied through an oil hole penetrating from the inner diameter surface to the outer diameter surface of the inner ring by centrifugal force. (For example, Patent Document 1).
Here, Dmn is calculated by rolling element PCD [mm] × rotational speed [min −1 ].

前掲の特許文献１のようなアンダーレース潤滑方式を採用した単列円筒ころ軸受の中には、図７に示すように、内輪１０１に形成されたラジアル方向の油穴１０２が、ころの軌道１０３よりもアキシアル方向で軸方向外側に位置する部分を通って内径面１０４から鍔外径面１０５まで貫通しており、内輪１０１の鍔外径面１０５に開口する油穴１０２の油出口がかご形保持器の円環部１０６の内方に位置している構成のものがある。   In the single row cylindrical roller bearing adopting the under-lace lubrication system as described in the above-mentioned Patent Document 1, as shown in FIG. 7, a radial oil hole 102 formed in the inner ring 101 is provided with a roller raceway 103. Further, the oil outlet of the oil hole 102 that passes through the portion positioned axially outside in the axial direction from the inner diameter surface 104 to the outer diameter surface 105 of the inner ring 101 and opens to the outer diameter surface 105 of the inner ring 101 is a cage shape. There exists a thing of the structure located inside the annular part 106 of a holder | retainer.

特開２００２−６６８７４号公報JP 2002-66874 A

しかしながら、図７の単列円筒ころ軸受の場合、油穴１０２の油出口から内輪１０１と円環部１０６との間に供給された潤滑剤が円環部１０６の内径面にあたって軸受内外に分離するため、軸受内に要求される量よりも多い潤滑剤を油穴１０２に供給する必要がある。   However, in the case of the single-row cylindrical roller bearing of FIG. 7, the lubricant supplied between the inner ring 101 and the annular portion 106 from the oil outlet of the oil hole 102 is separated into the inside and outside of the bearing on the inner surface of the annular portion 106. Therefore, it is necessary to supply more lubricant to the oil hole 102 than is required in the bearing.

そこで、本出願人は、本願出願時で未公開ながら、係る欠点を解決に貢献する先行技術として、前記円環部の内径面を軸方向の中央側が大径となるテーパ部に形成した転がり軸受を提案している（特願２００５−１３８３３０号）。この構成のかご形保持器によれば、内輪と保持器の円環部との間にある潤滑剤は、円環部のテーパ部から軸受内に向けて流れ易くなり、効率よく潤滑剤を供給することができる。   Therefore, the present applicant, as a prior art that has not been disclosed at the time of filing of the present application, contributes to solving the above drawbacks, a rolling bearing in which the inner diameter surface of the annular portion is formed in a tapered portion having a large diameter in the center in the axial direction. (Japanese Patent Application No. 2005-138330). According to the cage cage of this configuration, the lubricant between the inner ring and the annular portion of the cage can easily flow from the tapered portion of the annular portion into the bearing, and efficiently supplies the lubricant. can do.

ここで、軸受幅が同一の単列玉軸受と単列円筒ころ軸受を比較して考えると、円筒ころのころ長さは玉径に比して長いため、かご形保持器の円環部幅は玉保持器の円環部幅よりも狭い。したがって、内輪案内方式のかご形保持器を備えた単列円筒ころ軸受に上記先行技術を採用する場合、円環部の内径面にテーパ部の幅を大きく形成すると、内輪の保持器案内面に対向する円環部側の案内面を確保することができず、安定した回転が得られず、かご形保持器の高速回転を妨げる原因になる。また、円環部側の案内面に対するテーパ部の傾斜角を大きくすると、円環部の肉落ち量が多くなり、遠心力に対する円環部の強度が低下し、かご形保持器の高速回転を妨げる原因になる。   Here, considering the comparison between single-row ball bearings and single-row cylindrical roller bearings with the same bearing width, the roller length of cylindrical rollers is longer than the ball diameter. Is narrower than the ring width of the ball cage. Therefore, when the above-mentioned prior art is adopted for a single row cylindrical roller bearing equipped with a cage-type cage for the inner ring guide, if the width of the tapered portion is formed large on the inner diameter surface of the annular portion, the cage guide surface of the inner ring is formed. A guide surface on the opposite annular portion side cannot be secured, and stable rotation cannot be obtained, causing high-speed rotation of the cage retainer. In addition, if the inclination angle of the tapered portion with respect to the guide surface on the annular portion side is increased, the thickness of the annular portion increases, the strength of the annular portion against centrifugal force decreases, and high speed rotation of the cage retainer It becomes a cause to hinder.

そこで、この発明の課題は、内輪案内方式のかご形保持器を備えた単列円筒ころ軸受において、内輪とかご形保持器の円環部との間から軸受外に流出する潤滑剤を減少させながら、安定した高速運転を図ることにある。   Accordingly, an object of the present invention is to reduce lubricant flowing out of the bearing from between the inner ring and the annular portion of the cage retainer in the single row cylindrical roller bearing having the cage retainer of the inner ring guide system. However, stable high-speed operation is intended.

上記の課題を達成するため、この発明は、内輪と、外輪と、一対の円環部と柱部とからなるかご形保持器とを備え、前記かご形保持器は、単列の円筒ころを保持する高速回転用単列円筒ころ軸受において、前記円環部の内径面は、軸方向の中央側が大径となるテーパ部とこのテーパ部よりも軸方向外側で前記内輪の保持器案内面に対向する案内面とを有しており、前記円筒ころのころ長さＬｗ（単位：ｍｍ）と軸受幅Ｂとの比Ｌｗ／Ｂが０．３≦Ｌｗ／Ｂ＜０．４であり、前記円環部の幅Ｌ（単位：ｍｍ）が（Ｂ−Ｌｗ−１）／２であり、前記案内面の幅Ｌ１（単位：ｍｍ）がＬ１≧Ｌ×０．２であり、前記案内面に対する前記テーパ部の傾斜角θ（単位：度）がθ≦１０である構成を採用したものである。   In order to achieve the above object, the present invention comprises an inner ring, an outer ring, and a cage retainer composed of a pair of annular portions and a column portion, and the cage retainer comprises a single row of cylindrical rollers. In the single-row cylindrical roller bearing for high-speed rotation to be held, an inner diameter surface of the annular portion is a taper portion having a large diameter at the center side in the axial direction and a cage guide surface of the inner ring outside the taper portion in the axial direction. And the ratio Lw / B of the roller length Lw (unit: mm) of the cylindrical roller to the bearing width B is 0.3 ≦ Lw / B <0.4, The width L (unit: mm) of the annular portion is (B−Lw−1) / 2, the width L1 (unit: mm) of the guide surface is L1 ≧ L × 0.2, and the width relative to the guide surface is A configuration in which the inclination angle θ (unit: degree) of the tapered portion is θ ≦ 10 is adopted.

具体的には、かご形保持器の幅寸法の限界は軸受幅Ｂにより決まるため、円環部の幅寸法を得るべく、円筒ころのころ長さＬｗを小さくした。ここで、軸受幅Ｂは内輪と外輪の幅寸法が異なる場合、いずれか大きい方の寸法とする。前記円筒ころのころ長さＬｗ（単位：ｍｍ）と軸受幅Ｂとの比Ｌｗ／Ｂが０．３≦Ｌｗ／Ｂ＜０．４であり、前記円環部の幅Ｌ（単位：ｍｍ）が（Ｂ−Ｌｗ−１）／２である構成の採用により、単列円筒ころのころ長さを可及的に小さくしつつ、円筒ころの基本動定格荷重が単列玉軸受よりも比較的に小さくなることを防止し、円環部の幅を軸受幅Ｂに対し最大限に得られるようにした。ここで、軸受幅Ｂから１ｍｍを減算したのは、かご形保持器がその軸方向動により軸受幅から突出しないようにするための安全値である。
さらに、前記円環部の幅Ｌ（単位：ｍｍ）が（Ｂ−Ｌｗ−１）／２であり、前記案内面の幅Ｌ１（単位：ｍｍ）がＬ１≧Ｌ×０．２であり、前記案内面に対する前記テーパ部の傾斜角θ（単位：度）がθ≦１０である構成の採用により、内輪とかご形保持器の円環部との間から軸受外に流出する潤滑剤をテーパ部で減少させながら、内輪案内方式に十分な保持器側の案内面を得、加えて、円環部の肉落ちを最低限として遠心力に対する保持器強度を可及的に高めた。
したがって、この発明は、内輪案内方式のかご形保持器を備えた単列円筒ころ軸受において、内輪と保持器の円環部との間から軸受外に流出する潤滑剤を減少させながら、安定した高速運転を図ることができる。 Specifically, since the limit of the width dimension of the cage retainer is determined by the bearing width B, the roller length Lw of the cylindrical roller is reduced to obtain the width dimension of the annular portion. Here, when the width dimension of the inner ring and the outer ring is different, the bearing width B is set to the larger dimension. The ratio Lw / B between the roller length Lw (unit: mm) of the cylindrical roller and the bearing width B is 0.3 ≦ Lw / B <0.4, and the width L (unit: mm) of the annular portion. (B-Lw-1) / 2 makes it possible to make the roller length of the single row cylindrical roller as small as possible, while the basic dynamic load rating of the cylindrical roller is relatively higher than that of the single row ball bearing. It was made possible to obtain the maximum width of the annular portion with respect to the bearing width B. Here, 1 mm is subtracted from the bearing width B, which is a safety value for preventing the cage cage from protruding from the bearing width due to its axial movement.
Further, the width L (unit: mm) of the annular portion is (B-Lw-1) / 2, the width L1 (unit: mm) of the guide surface is L1 ≧ L × 0.2, and By adopting a configuration in which the inclination angle θ (unit: degree) of the tapered portion with respect to the guide surface is θ ≦ 10, the lubricant flowing out of the bearing from between the inner ring and the annular portion of the cage retainer is tapered. As a result, the cage-side guide surface sufficient for the inner ring guide system was obtained. In addition, the cage strength against centrifugal force was increased as much as possible while minimizing the thickness of the annular portion.
Therefore, according to the present invention, in the single row cylindrical roller bearing provided with the cage-type cage of the inner ring guide type, the lubricant flowing out of the bearing from between the inner ring and the annular portion of the cage is reduced and stabilized. High speed operation can be achieved.

以下、この発明の一実施例を添付図面に基づいて説明する。
この実施形態に係る高速回転用単列円筒ころ軸受は、図１、図２に示すように、内輪１と、外輪２と、一対の円環部１１、１１と柱部１２とからなるかご形保持器３とを備えている。かご形保持器３には、一対の円環部１１、１１と柱部１２とで単列の円筒ころ４を保持するポケット１３が形成されている。内輪１には単列の軌道５が形成されており、その両側に円筒ころ４の端面を案内する鍔が一体に形成されている。 Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.
The single-row cylindrical roller bearing for high-speed rotation according to this embodiment has a cage shape comprising an inner ring 1, an outer ring 2, a pair of annular parts 11, 11 and a column part 12, as shown in FIGS. And a cage 3. The cage retainer 3 is formed with a pocket 13 for holding a single row of cylindrical rollers 4 with a pair of annular portions 11 and 11 and a column portion 12. A single-row track 5 is formed on the inner ring 1, and flanges for guiding the end face of the cylindrical roller 4 are integrally formed on both sides thereof.

円環部１１の内径面は、軸方向の中央側が大径となる断面テーパ部１１ａとこのテーパ部１１ａよりも軸方向外側で前記内輪１の鍔外径面（保持器案内面）に対向する円筒案内面１１ｂとを有する。なお、内輪１の鍔外径面には、従来例と同様の油穴が適宜に穿たれている。   The inner diameter surface of the annular portion 11 faces the outer diameter surface (cage guide surface) of the inner ring 1 on the outer side in the axial direction with respect to the tapered section 11a having a large diameter on the center side in the axial direction. And a cylindrical guide surface 11b. In addition, an oil hole similar to the conventional example is appropriately drilled in the outer diameter surface of the inner ring 1.

一対の円環部１１の外径面と各柱部１２の外径面との間には、周方向の凹溝１４が形成されている。この凹溝１４は、ポケット１３内に流入した潤滑剤が遠心力によりかご形保持器３の外径面に排出され易くするために形成されている。   A circumferential groove 14 is formed between the outer diameter surface of the pair of annular portions 11 and the outer diameter surface of each column portion 12. The concave groove 14 is formed so that the lubricant that has flowed into the pocket 13 can be easily discharged to the outer diameter surface of the cage retainer 3 by centrifugal force.

各ポケット１３は、円筒ころ４の端面を案内する一対の軸方向側面１３ａと、一対の軸方向側面１３ａのラジアル方向辺と周方向に連続するぬすみ部１３ｂと、ぬすみ部１３ｂ間に連続し、円筒ころ４を周方向に等配する一対の周方向側面１３ｃとで形成されている。   Each pocket 13 is continuous between a pair of axial side surfaces 13a for guiding the end surface of the cylindrical roller 4, a radial portion of the pair of axial side surfaces 13a and a thin portion 13b continuous in the circumferential direction, and the thin portion 13b. The cylindrical roller 4 is formed by a pair of circumferential side surfaces 13c equally arranged in the circumferential direction.

実施例に係る高速回転用単列円筒ころ軸受の各寸法を以下に述べる。
軸受幅Ｂは、２４（ｍｍ）であり、内輪１、外輪２とも同一幅である。
軸受外径は１５０（ｍｍ）、軸受内径は１００（ｍｍ）である。
軸受断面高さＣ：（軸受外径−軸受内径）／２は２５（ｍｍ）である。 Each dimension of the single row cylindrical roller bearing for high speed rotation according to the embodiment will be described below.
The bearing width B is 24 (mm), and both the inner ring 1 and the outer ring 2 have the same width.
The outer diameter of the bearing is 150 (mm), and the inner diameter of the bearing is 100 (mm).
Bearing cross section height C: (bearing outer diameter−bearing inner diameter) / 2 is 25 (mm).

円筒ころの直径Ｄａは９（ｍｍ）であり、円筒ころのころ長さＬｗは９（ｍｍ）である。   The diameter Da of the cylindrical roller is 9 (mm), and the roller length Lw of the cylindrical roller is 9 (mm).

比Ｄａ／Ｃは０．３６、比Ｌｗ／Ｂは０．３７５となっている。この数値の採用により、軸受の高速運転化、かつ軸受の低温度上昇化を図ることができる。なお、この技術は、特開２００３−２７８７４６号公報に詳しく開示されている。   The ratio Da / C is 0.36, and the ratio Lw / B is 0.375. By adopting this numerical value, the bearing can be operated at high speed and the temperature of the bearing can be lowered. This technique is disclosed in detail in Japanese Patent Application Laid-Open No. 2003-278746.

円環部１１の内外径間の長さである保持器高さＨは５．９（ｍｍ）である。   The cage height H, which is the length between the inner and outer diameters of the annular portion 11, is 5.9 (mm).

ポケット１３の軸方向側面１３ａと、この側面１３ａの軸方向外側に位置する円環部１１の幅面との間の長さである円環部の幅Ｌは７．５（ｍｍ）である。   The width L of the annular portion, which is the length between the axial side surface 13a of the pocket 13 and the width surface of the annular portion 11 located on the outer side in the axial direction of the side surface 13a, is 7.5 (mm).

上記テーパ部１１ａの軸方向外側辺に連続する円筒案内面１１ｂの幅Ｌ１は、円環部の幅Ｌ×０．２の値：１．５（ｍｍ）となっている。円筒案内面１１ｂに対するテーパ部１１ａの傾斜角θは５度である。   The width L1 of the cylindrical guide surface 11b continuous to the outer side in the axial direction of the tapered portion 11a is a value of the width L × 0.2 of the annular portion: 1.5 (mm). The inclination angle θ of the tapered portion 11a with respect to the cylindrical guide surface 11b is 5 degrees.

上記かご形保持器３は、全体がポリエーテルエーテルケトン（ＰＥＥＫ）製の一体成形保持器となっており、射出成形または、旋削加工となっている。   The cage-type cage 3 is an integral molded cage made of polyether ether ketone (PEEK) as a whole, and is injection-molded or turned.

図３に示す比較例１は、円環部の幅Ｌが４．０５（ｍｍ）となっている点で上記実施例と相違するものである。
図３と図１を対比すれば明らかなように、比較例１では、円筒案内面３１ｂが大き過ぎてテーパ部３１ａを十分に形成することができない。 Comparative Example 1 shown in FIG. 3 differs from the above example in that the width L of the annular portion is 4.05 (mm).
As is clear from the comparison between FIG. 3 and FIG. 1, in the first comparative example, the cylindrical guide surface 31b is too large to sufficiently form the tapered portion 31a.

図４に示す比較例２は、円筒案内面４１ｂの幅Ｌ１が５．８（ｍｍ）、円筒ころの直径Ｄａが１１（ｍｍ）、円筒ころのころ長さＬｗが１１（ｍｍ）である点で上記実施例と相違し、この相違点に伴う軸受の各寸法の変更により、比Ｄａ／Ｃが０．４４、比Ｌｗ／Ｂが０．４６となっているものである。この比較例２では、比Ｌｗ／Ｂが０．４を超えるため、高速回転かつ低温度上昇を十分に達成することができない。   In the comparative example 2 shown in FIG. 4, the width L1 of the cylindrical guide surface 41b is 5.8 (mm), the diameter Da of the cylindrical roller is 11 (mm), and the roller length Lw of the cylindrical roller is 11 (mm). Thus, the ratio Da / C is 0.44 and the ratio Lw / B is 0.46 due to the change in each dimension of the bearing accompanying this difference. In Comparative Example 2, since the ratio Lw / B exceeds 0.4, high speed rotation and low temperature rise cannot be sufficiently achieved.

図５に示す比較例３は、円筒案内面５１ｂの幅Ｌ１がＬ×０．５の値：３．７５（ｍｍ）になっており、円筒案内面５１ｂに対するテーパ部５１ａの傾斜角θが２０度である点で上記実施例と相違するものである。
図５と図１（ｂ）を対比すれば明らかなように、比較例３は、円環部５１の肉落ち量が多くなり、保持器強度が低い。 In Comparative Example 3 shown in FIG. 5, the width L1 of the cylindrical guide surface 51b is a value of L × 0.5: 3.75 (mm), and the inclination angle θ of the tapered portion 51a with respect to the cylindrical guide surface 51b is 20. It is different from the above embodiment in that it is a degree.
As is clear from a comparison between FIG. 5 and FIG. 1B, in Comparative Example 3, the thickness of the annular portion 51 is increased and the cage strength is low.

図６に示す比較例４は、円筒案内面６１ｂの幅Ｌ１がＬ×０．１の値：０．７５（ｍｍ）になっている点で上記実施例と相違するものである。
図６と図１（ｂ）を対比すれば明らかなように、比較例４は、円筒案内面６１ｂが殆どなくなり、安定した案内を得ることができない。 A comparative example 4 shown in FIG. 6 is different from the above-described embodiment in that the width L1 of the cylindrical guide surface 61b is a value of L × 0.1: 0.75 (mm).
As is clear from the comparison between FIG. 6 and FIG. 1B, the comparative example 4 has almost no cylindrical guide surface 61b, and stable guidance cannot be obtained.

（ａ）実施例に係る単列円筒ころ軸受の要部断面図、（ｂ）実施例に係るかご形保持器の部分拡大断面図(A) Main part sectional drawing of the single row cylindrical roller bearing which concerns on an Example, (b) The partial expanded sectional view of the cage-type cage which concerns on an Example 図１のかご形保持器の全体斜視図Overall perspective view of the cage retainer of FIG. 比較例１の要部断面図Cross-sectional view of the main part of Comparative Example 1 比較例２の要部断面図Sectional drawing of the principal part of the comparative example 2 比較例３のかご形保持器の部分拡大断面図Partial expanded sectional view of the cage retainer of Comparative Example 3 比較例４のかご形保持器の部分拡大断面図Partial expanded sectional view of the cage retainer of Comparative Example 4 従来例の要部断面図Cross section of the main part of the conventional example

符号の説明Explanation of symbols

１ 内輪
２ 外輪
３ かご形保持器
４ 円筒ころ
５ 軌道
１１ 円環部
１１ａ テーパ部
１１ｂ 円筒案内面
１２ 柱部
１３ ポケット DESCRIPTION OF SYMBOLS 1 Inner ring 2 Outer ring 3 Cage-shaped cage 4 Cylindrical roller 5 Track 11 Ring part 11a Tapered part 11b Cylindrical guide surface 12 Column part 13 Pocket

Claims (1)

内輪と、外輪と、一対の円環部と柱部とからなるかご形保持器とを備え、前記かご形保持器は、単列の円筒ころを保持する高速回転用単列円筒ころ軸受において、
前記円環部の内径面は、軸方向の中央側が大径となる断面テーパ部とこのテーパ部よりも軸方向外側で前記内輪の保持器案内面に対向する案内面とを有しており、前記円筒ころのころ長さＬｗ（単位：ｍｍ）と軸受幅Ｂとの比Ｌｗ／Ｂが０．３≦Ｌｗ／Ｂ＜０．４であり、前記円環部の幅Ｌ（単位：ｍｍ）が（Ｂ−Ｌｗ−１）／２であり、前記案内面の幅Ｌ１（単位：ｍｍ）がＬ１≧Ｌ×０．２であり、前記案内面に対する前記テーパ部の傾斜角θ（単位：度）がθ≦１０であることを特徴とする高速回転用単列円筒ころ軸受。 An inner ring, an outer ring, and a cage-shaped cage composed of a pair of annular portions and column portions, the cage-shaped cage is a single-row cylindrical roller bearing for high-speed rotation that holds a single-row cylindrical roller,
The inner diameter surface of the annular portion has a tapered section with a central diameter in the axial direction and a guide surface facing the cage guide surface of the inner ring on the outer side in the axial direction than the tapered portion, The ratio Lw / B between the roller length Lw (unit: mm) of the cylindrical roller and the bearing width B is 0.3 ≦ Lw / B <0.4, and the width L (unit: mm) of the annular portion. Is (B−Lw−1) / 2, the width L1 (unit: mm) of the guide surface is L1 ≧ L × 0.2, and the inclination angle θ (unit: degree) of the tapered portion with respect to the guide surface ) Is θ ≦ 10, a single-row cylindrical roller bearing for high-speed rotation.
JP2006175370A 2006-06-26 2006-06-26 High-speed rotation single row cylindrical roller bearing Pending JP2008002659A (en)

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WO2010073867A1 (en) * 2008-12-26 2010-07-01 Ntn株式会社 Railroad vehicle drive unit
FR2981999A1 (en) * 2011-10-28 2013-05-03 Ntn Snr Roulements Massive cage for separating traveling bodies of bearing unit to be mounted on central propeller shaft of railway vehicle, has junction zones forming off-hook by reducing thickness of side rings and connecting peripheral zones to bridges
KR20130137471A (en) * 2012-06-07 2013-12-17 한국전력공사 Device for removal of slag
EP2956684A4 (en) * 2013-02-14 2016-11-30 New Hampshire Ball Bearings Angular contact ball bearing
CN106762151A (en) * 2016-11-29 2017-05-31 沈阳黎明航空发动机(集团)有限责任公司 A kind of aeroplane engine main bearing inner ring integral structure
US10260563B2 (en) 2017-05-18 2019-04-16 General Electric Company Bearing cages for roller bearing assemblies
US10451113B2 (en) 2017-05-18 2019-10-22 General Electric Company Bearing cages for roller bearing assemblies

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JP2001082464A (en) * 1999-09-13 2001-03-27 Nsk Ltd Cylindrical roller bearing
JP2001165178A (en) * 1999-12-10 2001-06-19 Koyo Seiko Co Ltd Rolling bearing
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Publication number Priority date Publication date Assignee Title
WO2010073867A1 (en) * 2008-12-26 2010-07-01 Ntn株式会社 Railroad vehicle drive unit
FR2981999A1 (en) * 2011-10-28 2013-05-03 Ntn Snr Roulements Massive cage for separating traveling bodies of bearing unit to be mounted on central propeller shaft of railway vehicle, has junction zones forming off-hook by reducing thickness of side rings and connecting peripheral zones to bridges
KR20130137471A (en) * 2012-06-07 2013-12-17 한국전력공사 Device for removal of slag
EP2956684A4 (en) * 2013-02-14 2016-11-30 New Hampshire Ball Bearings Angular contact ball bearing
CN106762151A (en) * 2016-11-29 2017-05-31 沈阳黎明航空发动机(集团)有限责任公司 A kind of aeroplane engine main bearing inner ring integral structure
US10260563B2 (en) 2017-05-18 2019-04-16 General Electric Company Bearing cages for roller bearing assemblies
US10451113B2 (en) 2017-05-18 2019-10-22 General Electric Company Bearing cages for roller bearing assemblies

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