JP2008138841A - Tandem type double row angular contact ball bearing - Google Patents

Tandem type double row angular contact ball bearing Download PDF

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JP2008138841A
JP2008138841A JP2006328420A JP2006328420A JP2008138841A JP 2008138841 A JP2008138841 A JP 2008138841A JP 2006328420 A JP2006328420 A JP 2006328420A JP 2006328420 A JP2006328420 A JP 2006328420A JP 2008138841 A JP2008138841 A JP 2008138841A
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diameter side
ball
double
row angular
ball bearing
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JP4722822B2 (en
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Yasuyuki Katayama
康行 片山
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3806—Details of interaction of cage and race, e.g. retention, 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/182—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact in tandem 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • F16C2240/34—Contact angles
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]

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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 tandem type double row angular contact ball bearing, without damaging a cage, while reducing the size. <P>SOLUTION: This tandem type double row angular contact ball bearing has an inner race 12 having raceway surfaces 11a and 11b of double rows, an outer race having raceway surfaces 13a and 13b of double rows corresponding to the raceway surfaces 11a and 11b of the inner race 12, and ball groups 15 and 16 of double rows interposed with respectively different pitch circle diameters D1 and D2 between the raceway surfaces 11a, 11b, 13a and 13b of the respective rows of the inner race 12 and the outer race 14. A large diameter side ball contact angle α1 is made different from a small diameter side ball contact angle α2, and a difference in a revolving rotating speed between a large diameter side ball 27 and a small diameter side ball 28, is set to 10% or less. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、タンデム型複列アンギュラ玉軸受に関する。   The present invention relates to a tandem type double row angular contact ball bearing.

軸受には、ラジアル荷重と一方向のアキシアル荷重を負荷することができるアンギュラ玉軸受がある。玉（ボール）と内輪・外輪とは接触角をもっており、接触角が大きくなるほどアキシアル荷重の負荷能力が大きくなり,接触角が小さいほど、 高速回転に有利となる。   As the bearing, there is an angular ball bearing capable of applying a radial load and an axial load in one direction. Balls and inner and outer rings have a contact angle. The larger the contact angle, the greater the load capacity of the axial load. The smaller the contact angle, the more advantageous for high-speed rotation.

ところで、転がり抵抗を低減するために、円すいころ軸受に代わるものとして複列アンギュラ玉軸受（タンデム型）がある（特許文献１）。また、このタンデム型複列アンギュラ玉軸受を自動車のトランスファに使用したものがある（特許文献２）。なお、トランスファとは、４ＷＤ車で、トランスミッションから来る動力を前後輪に分けて伝える装置であり、通常はデファレンシャル装置（差動装置）も一緒に組み込まれており、これを総称してセンターデフと呼んでいる。また、複列アンギュラ玉軸受とは、単列アンギュラ玉軸受を背面組合せとし、内輪、外輪をそれぞれ一体にした構造で、両方向のアキシアル荷重を負荷することができ、しかも、 モーメント荷重に対する負荷能力がある軸受である。   By the way, in order to reduce rolling resistance, there is a double row angular contact ball bearing (tandem type) as an alternative to the tapered roller bearing (Patent Document 1). In addition, there is one in which this tandem type double row angular ball bearing is used for an automobile transfer (Patent Document 2). A transfer is a 4WD vehicle that transmits the power coming from the transmission to the front and rear wheels. Usually, a differential device (differential device) is also built in. I'm calling. A double row angular contact ball bearing is a structure in which a single row angular contact ball bearing is combined on the back and the inner ring and outer ring are integrated together, and can carry axial loads in both directions. It is a certain bearing.

タンデム型複列アンギュラ玉軸受は、図３に示すように、複列の軌道面１ａ、１ｂを有する内輪２と、この内輪２の軌道面１ａ、１ｂと対応する複列の軌道面３ａ、３ｂを有する外輪４と、内輪２および外輪４の各列の軌道面１ａ、１ｂ、３ａ、３ｂ間に介装される複列の玉群５、６とを備える。複列の玉群５、６は、それぞれ異なるピッチ円直径をもっている。また、各玉群５、６のボール７，８は内輪２と外輪４との間に配置される保持器９，１０に保持されている。
特許第１８１５４７号 特開２００４−１８３７４５号公報 As shown in FIG. 3, the tandem double-row angular contact ball bearing includes an inner ring 2 having double-row raceway surfaces 1a and 1b, and double-row raceway surfaces 3a and 3b corresponding to the raceway surfaces 1a and 1b of the inner ring 2. And an outer ring 4 and a double-row ball group 5, 6 interposed between the raceways 1a, 1b, 3a, 3b of each row of the inner ring 2 and the outer ring 4. The double row ball groups 5 and 6 have different pitch circle diameters. The balls 7 and 8 of each ball group 5 and 6 are held by cages 9 and 10 disposed between the inner ring 2 and the outer ring 4.
Patent No. 181547 JP 2004-183745 A

すなわち、タンデム型複列アンギュラ玉軸受は、内輪２とボール７、８と保持器９、１０とのアセンブリ体と、外輪４とが分離できる構造となっているので、その取り扱いは円すいころ軸受と同様であり、取り扱いやすい。そこで、近年では、低トルク化を目的に円すいころ軸受に代えてこのタンデム型複列アンギュラ玉軸受が使用されている。   That is, the tandem double-row angular contact ball bearing has a structure in which the assembly of the inner ring 2 and the balls 7 and 8 and the cages 9 and 10 and the outer ring 4 can be separated from each other. It is the same and easy to handle. Therefore, in recent years, this tandem type double-row angular ball bearing is used in place of the tapered roller bearing for the purpose of reducing the torque.

ところが、タンデム型複列アンギュラ玉軸受は、円錐ころ軸受と同等の負荷容量や剛性を確保しようとすると、軸受サイズが大きくなる。また、タンデム型複列アンギュラ玉軸受はデファレンシャル装置などで使用された場合、デファレンシャル装置のピニオン軸は最大７０００ｒｐｍで回転する。そのため、この回転数では、タンデム型複列アンギュラ玉軸受の両軌道溝（軌道面）で相対すべりが発生し、保持器にダメージを与える。   However, the tandem double-row angular contact ball bearing has a large bearing size in order to ensure the same load capacity and rigidity as the tapered roller bearing. Further, when the tandem double-row angular ball bearing is used in a differential device or the like, the pinion shaft of the differential device rotates at a maximum of 7000 rpm. For this reason, at this rotational speed, relative slip occurs in both raceway grooves (track surfaces) of the tandem double-row angular contact ball bearing, which damages the cage.

本発明は、上記課題に鑑みて、コンパクト化を図ることができて、しかも保持器にダメージを与えないタンデム型複列アンギュラ玉軸受を提供する。   In view of the above problems, the present invention provides a tandem double-row angular ball bearing that can be made compact and that does not damage the cage.

本発明のタンデム型複列アンギュラ玉軸受は、複列の軌道面を有する内輪と、この内輪の軌道面と対応する複列の軌道面を有する外輪と、内輪および外輪の各列の軌道面間に、それぞれ異なるピッチ円直径をもって介装される複列の玉群とを備えたタンデム型複列アンギュラ玉軸受において、大径側のボール接触角と小径側のボール接触角とを相違させて、大径側のボールと小径側のボールとの公転回転数の差を１０％以下に設定したものである。   The tandem double-row angular contact ball bearing of the present invention includes an inner ring having a double-row raceway surface, an outer ring having a double-row raceway surface corresponding to the raceway surface of the inner ring, and a raceway surface between each row of the inner ring and the outer ring. Further, in the tandem type double row angular contact ball bearing provided with a double row ball group interposed with different pitch circle diameters, the ball contact angle on the large diameter side is different from the ball contact angle on the small diameter side, The difference in revolution speed between the large-diameter side ball and the small-diameter side ball is set to 10% or less.

本発明のタンデム型複列アンギュラ玉軸受によれば、大径側のボールと小径側のボールとの公転回転数の差を１０％以下に設定したものであるので、大径側の保持器の回転速度（回転数）と小径側の保持器の回転速度（回転数）とが略等しくなる。   According to the tandem double-row angular contact ball bearing of the present invention, the difference in revolution speed between the large-diameter side ball and the small-diameter side ball is set to 10% or less. The rotation speed (number of rotations) is substantially equal to the rotation speed (number of rotations) of the cage on the small diameter side.

大径側のボール保持器と小径側のボール保持器とが接触するものであっても、大径側のボール保持器と小径側のボール保持器とが一体化されたものであってもよい。   The large-diameter side ball cage and the small-diameter side ball cage may be in contact with each other, or the large-diameter side ball cage and the small-diameter side ball cage may be integrated. .

本発明では、大径側の保持器回転数と小径側の保持器回転数は略等しくなるので、保持器同士が接触しても円滑な転がり運動が妨げられることがなくなって、保持器にダメージを与えない。このため、保持器同士が近接した状態乃至接触した状態で配置することができて、軸方向長さのコンパクト化を図ることができる。   In the present invention, since the cage rotation speed on the large diameter side and the cage rotation speed on the small diameter side are substantially equal, smooth rolling motion is not hindered even if the cages come into contact with each other, and the cage is damaged. Not give. For this reason, it can arrange | position in the state which the holder | retainer adjoined thru | or the state which contacted, and can achieve size reduction of an axial direction length.

ところで、保持器回転数はピッチ円径も一つの因子を含んだ演算式にて算出することができるので、このピッチ円径を調整することによっても、大径側と小径側とにおいて、公転回転数の差を１０％以下に設定することが可能である。しかしながら、ピッチ円径での調整では、鋼球（ボール）のサイズ（大きさ）が通常決まっており微調整が困難であるため、内外輪の肉厚等の関係から軸受サイズに影響を与える可能性があり、好ましくない。これに対して、本発明のように、大径側のボール接触角と小径側のボール接触角とを相違させることによって、ボールの公転回転数を調整すれば、軸受サイズを大きくする必要がなく、軸受全体の軸方向長さの大型化を防止できる。   By the way, the cage rotation speed can be calculated by an arithmetic expression including one factor of the pitch circle diameter. Therefore, by adjusting the pitch circle diameter, the revolution rotation can be performed on the large diameter side and the small diameter side. The difference in number can be set to 10% or less. However, since the size of the steel ball (ball) is usually determined and fine adjustment is difficult in the adjustment with the pitch circle diameter, the bearing size can be affected due to the wall thickness of the inner and outer rings. This is undesirable. On the other hand, if the revolution speed of the ball is adjusted by making the ball contact angle on the large diameter side different from the ball contact angle on the small diameter side as in the present invention, there is no need to increase the bearing size. Therefore, it is possible to prevent an increase in the axial length of the entire bearing.

大径側の保持器と小径側の保持器とを一体化することによって、軸方向長さの一層のコンパクト化を図ることができる。   By integrating the retainer on the large diameter side and the retainer on the small diameter side, it is possible to further reduce the axial length.

以下本発明の実施の形態を図１と図２に基づいて説明する。   Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

図１に第１実施形態のタンデム型複列アンギュラ玉軸受を示し、このタンデム型複列アンギュラ玉軸受は、複列の軌道面１１ａ、１１ｂを有する内輪１２と、この内輪１２の軌道面１１ａ、１１ｂと対応する複列の軌道面１３ａ、１３ｂを有する外輪１４と、内輪１２および外輪１４の各列の軌道面１１ａ、１１ｂ、１３ａ、１３ｂ間に介装される複列の玉群１５、１６とを備える。玉群１５、１６はそれぞれ異なるピッチ円径（ピッチ円直径：ＰＣＤ）Ｄ１、Ｄ２をもっている。この場合、Ｄ１＞Ｄ２とされる。   FIG. 1 shows a tandem double-row angular contact ball bearing according to the first embodiment. The tandem double-row angular contact ball bearing includes an inner ring 12 having double-row raceway surfaces 11a and 11b, and a raceway surface 11a of the inner ring 12; The outer ring 14 having double-row raceway surfaces 13a and 13b corresponding to 11b, and the double-row ball groups 15 and 16 interposed between the raceways 11a, 11b, 13a and 13b of each row of the inner ring 12 and the outer ring 14 With. The ball groups 15, 16 have different pitch circle diameters (pitch circle diameter: PCD) D1, D2. In this case, D1> D2.

内輪１２は、その外径面に第１切欠部２１が形成されるとともに、この第１切欠部２１に第２切欠部２２が形成される。そして、第１切欠部２１の第２切欠部側の端部が前記軌道面１１ａとされ、第２切欠部２２が前記軌道面１１ｂとされる。また、第１切欠部２１の第２切欠部２２側には、周方向溝２３が形成されている。   The inner ring 12 has a first cutout portion 21 formed on the outer diameter surface thereof, and a second cutout portion 22 formed in the first cutout portion 21. And the edge part by the side of the 2nd notch of the 1st notch part 21 is made into the said track surface 11a, and the 2nd notch part 22 is made into the said track surface 11b. Further, a circumferential groove 23 is formed on the first notch 21 on the second notch 22 side.

外輪１４は、その内径面に第１切欠部２４が形成されるとともに、この第１切欠部２４に第２切欠部２５が形成される。第１切欠部２４の第２切欠部側の端部が前記軌道面１３ｂとされ、第２切欠部２５が前記軌道面１３ａとされる。   The outer ring 14 has a first notch 24 formed on the inner diameter surface thereof, and a second notch 25 is formed in the first notch 24. The end of the first notch 24 on the second notch side is the track surface 13b, and the second notch 25 is the track surface 13a.

玉群１５、１６のボールはそれぞれ保持器１９、２０にて保持される。大径側の保持器１９は、周方向に沿って所定ピッチでポケット４０が形成された短円筒体からなり、各ポケット４０に玉群１５を構成するボール（鋼球）２７が保持される。また、小径側の保持器２０は、周方向に沿って所定ピッチでポケット４１が形成された短円筒状の本体部４２と、この本体部４２の大径側端に設けられる内鍔部４３及び外鍔部４４とを備える。各ポケット４１に玉群１６を構成するボール（鋼球）２８が保持される。なお、保持器２０の内鍔部４３が内輪１２の周方向溝２３に嵌合している。   The balls of the ball groups 15 and 16 are held by cages 19 and 20, respectively. The large-diameter side retainer 19 is formed of a short cylindrical body in which pockets 40 are formed at a predetermined pitch along the circumferential direction, and balls (steel balls) 27 constituting the ball group 15 are held in each pocket 40. The small-diameter side retainer 20 includes a short cylindrical main body portion 42 in which pockets 41 are formed at a predetermined pitch along the circumferential direction, an inner flange portion 43 provided at the large-diameter side end of the main body portion 42, and And an outer casing 44. A ball (steel ball) 28 constituting the ball group 16 is held in each pocket 41. The inner flange 43 of the cage 20 is fitted in the circumferential groove 23 of the inner ring 12.

この保持器１９、２０は樹脂保持器である。この樹脂としてはエンジニアリングプラスチックが好ましい。ここで、エンジニアリングプラスチックとは、合成樹脂のなかで主に耐熱性が優れ、強度が必要とされる分野に使うことができるものであって、エンプラと略される。また、エンジニアリングプラスチックは、汎用エンジニアリングプラスチックとスーパーエンジニアリングプラスチックとがあり、この保持器１９，２０に用いるエンジニアリングプラスチックには両者を含む。以下に代表的なものを掲げる。なお、これらはエンジニアリングプラスチックの例示であって、エンジニアリングプラスチックが以下のものに限定されるものではない。また、この樹脂保持器１９，２０では、例えば射出成形にて形成することができる。   The cages 19 and 20 are resin cages. This resin is preferably an engineering plastic. Here, the engineering plastic is an abbreviation for engineering plastics, which is excellent in heat resistance among synthetic resins and can be used in fields where strength is required. Engineering plastics include general-purpose engineering plastics and super engineering plastics. The engineering plastics used for the cages 19 and 20 include both. The following are typical examples. These are examples of engineering plastics, and engineering plastics are not limited to the following. The resin holders 19 and 20 can be formed by, for example, injection molding.

汎用エンジニアリングプラスチックには、ポリカーボネート（ＰＣ）、ポリアミド６（ＰＡ６）、ポリアミド６６（ＰＡ６６）、ポリアセタール（ＰＯＭ）、変性ポリフェニレンエーテル（ｍ−ＰＰＥ）、ポリブチレンテレフタレート（ＰＢＴ）、ＧＦ強化ポリエチレンテレフタレート（ＧＦ−ＰＥＴ）、超高分子量ポリエチレン（ＵＨＭＷ−ＰＥ）等がある。また、スーパーエンジニアリングプラスチックには、ポリサルホン（ＰＳＦ）、ポリエーテルサルホン（ＰＥＳ）、ポリフェニレンサルファイド（ＰＰＳ）、ポリアリレート（ＰＡＲ）、ポリアミドイミド（ＰＡＩ）、ポリエーテルイミド（ＰＥＩ）、ポリエーテルエーテルケトン（ＰＥＥＫ）、液晶ポリマー（ＬＣＰ）、熱可塑性ポリイミド（ＴＰＩ）、ポリベンズイミダゾール（ＰＢＩ）、ポリメチルベンテン（ＴＰＸ）、ポリ１，４−シクロヘキサンジメチレンテレフタレート（ＰＣＴ）、ポリアミド４６（ＰＡ４６）、ポリアミド６Ｔ（ＰＡ６Ｔ）、ポリアミド９Ｔ（ＰＡ９Ｔ）、ポリアミド１１，１２ （ＰＡ１１，１２）、フッ素樹脂、ポリフタルアミド（ＰＰＡ）等がある。   General-purpose engineering plastics include polycarbonate (PC), polyamide 6 (PA6), polyamide 66 (PA66), polyacetal (POM), modified polyphenylene ether (m-PPE), polybutylene terephthalate (PBT), and GF reinforced polyethylene terephthalate (GF). -PET), ultra high molecular weight polyethylene (UHMW-PE) and the like. Super engineering plastics include polysulfone (PSF), polyethersulfone (PES), polyphenylene sulfide (PPS), polyarylate (PAR), polyamideimide (PAI), polyetherimide (PEI), polyetheretherketone. (PEEK), liquid crystal polymer (LCP), thermoplastic polyimide (TPI), polybenzimidazole (PBI), polymethylbenten (TPX), poly 1,4-cyclohexanedimethylene terephthalate (PCT), polyamide 46 (PA46), There are polyamide 6T (PA6T), polyamide 9T (PA9T), polyamide 11,12 (PA11,12), fluororesin, polyphthalamide (PPA) and the like.

この軸受では、大径側のボール接触角α１と小径側のボール接触角α２とを相違させて、大径側のボール２７と小径側のボール２８との公転回転数の差を１０％以下に設定している。この場合、図２に示すように、内輪１２の大径側の接触点ａと内輪１２の小径側の接触点ｂとを結ぶ線の延長線Ｌ１と、外輪１４の大径側の接触点ｃと外輪１４の小径側の接触点ｄとを結ぶ線の延長線Ｌ２と、軸受中心線Ｌとの交点が作用点５０となる。   In this bearing, the ball contact angle α1 on the large diameter side and the ball contact angle α2 on the small diameter side are made different so that the difference in revolution speed between the large diameter ball 27 and the small diameter ball 28 is 10% or less. It is set. In this case, as shown in FIG. 2, an extended line L1 of a line connecting the contact point a on the large diameter side of the inner ring 12 and the contact point b on the small diameter side of the inner ring 12 and the contact point c on the large diameter side of the outer ring 14. The point of action 50 is the intersection of the extension line L2 of the line connecting the contact point d on the small diameter side of the outer ring 14 and the bearing center line L.

ここで、軸受における軸受中心周りの転動体中心（保持器）の公転回転数は、次に示す数１の式で求めることができる。

Figure 2008138841
Here, the revolution speed of the rolling element center (retainer) around the bearing center in the bearing can be obtained by the following equation (1).
Figure 2008138841

このため、大径側と小径側とにおいて、接触角を相違させることによって、各保持器１９、２０の公転回転数を変更でき、大径側のボール２７と小径側のボール２８との公転回転数の差を１０％以下に設定することができる。   Therefore, by changing the contact angle between the large-diameter side and the small-diameter side, the revolution speed of the cages 19 and 20 can be changed, and the revolution rotation between the large-diameter side ball 27 and the small-diameter side ball 28 is achieved. The difference in number can be set to 10% or less.

本発明では、大径側の保持器回転数と小径側の保持器回転数は略等しくなるので、保持器１９、２０同士が接触しても円滑な転がり運動が妨げられることがなくなって、保持器１９、２０にダメージを与えない。このため、保持器１９、２０同士が近接した状態乃至接触した状態で配置することができて、軸方向長さのコンパクト化を図ることができる。   In the present invention, since the cage rotation speed on the large diameter side and the cage rotation speed on the small diameter side are substantially equal, even if the cages 19 and 20 are in contact with each other, the smooth rolling motion is not hindered and retained. Does not damage containers 19 and 20. For this reason, it can arrange | position in the state from which the holder | retainers 19 and 20 adjoined thru | or contacted, and can attain the compactization of axial direction length.

ところで、前記数１によれば、ピッチ円径を調整することによっても、大径側と小径側とにおいて、公転回転数の差を１０％以下に設定することが可能である。しかしながら、ピッチ円径での調整では、鋼球（ボール）のサイズ（大きさ）が通常決まっており微調整が困難であるため、内外輪の肉厚等の関係から軸受サイズに影響を与える可能性があり、好ましくない。これに対して、大径側のボール接触角と小径側のボール接触角とを相違させることによって、ボールの公転回転数を調整すれば、軸受サイズを大きくする必要がなく、軸受全体の軸方向長さの大型化を防止できる。   By the way, according to the above equation 1, it is possible to set the difference in revolution speed between the large diameter side and the small diameter side to 10% or less by adjusting the pitch circle diameter. However, since the size of the steel ball (ball) is usually determined and fine adjustment is difficult in the adjustment with the pitch circle diameter, the bearing size can be affected due to the wall thickness of the inner and outer rings. This is undesirable. On the other hand, if the ball contact angle on the large diameter side and the ball contact angle on the small diameter side are made different to adjust the revolution speed of the ball, there is no need to increase the bearing size, and the axial direction of the entire bearing An increase in length can be prevented.

なお、公転回転数の差としては無いのが好ましいが、１０％以下であれば、保持器同士が接触しても円滑な転がり運動が妨げられることはない。しかも、公転回転数の差を無くすように構成するには製造上困難性を有し、ある程度の差を有するものの方が製造しやすい利点がある。公転回転数の差が１０％を越えれば、円滑な転がり運動が妨げられるおそれがある。   In addition, it is preferable that it is not as a difference of revolution speed, but if it is 10% or less, even if a holder | retainer contacts, smooth rolling motion will not be prevented. In addition, it is difficult to manufacture the structure so as to eliminate the difference in revolution speed, and the one having a certain difference has an advantage that it is easy to manufacture. If the difference in revolution speed exceeds 10%, smooth rolling motion may be hindered.

このように、大径側の保持器１９と小径側の保持器２０とは接触していてもよいので、大径側の保持器１９と小径側の保持器２０とが一体化したものであってもよい。大径側の保持器１９と小径側の保持器２０とを一体化することによって、軸方向長さの一層のコンパクト化を図ることができる。   As described above, the large-diameter side retainer 19 and the small-diameter side retainer 20 may be in contact with each other, so that the large-diameter side retainer 19 and the small-diameter side retainer 20 are integrated. May be. By integrating the large-diameter side retainer 19 and the small-diameter side retainer 20, the axial length can be further reduced.

また、保持器１９，２０を樹脂保持器としているので、重量が軽く摩擦係数が小さいため、軸受起動時のトルク損失や保持器摩耗の低減に好適となる。特に、樹脂保持器では、射出成形で形成することができるので、特異形状の保持器でも製作し易い利点がある。   Further, since the cages 19 and 20 are resin cages, they are light in weight and have a small coefficient of friction, which is suitable for reducing torque loss and cage wear when starting the bearing. In particular, since the resin cage can be formed by injection molding, there is an advantage that even a cage having a unique shape can be easily manufactured.

以上、本発明の実施形態につき説明したが、本発明は前記実施形態に限定されることなく種々の変形が可能であって、例えば、玉群１５，１６のボール２７、２８の数、球径等は、同一球径であれば、任意に変更できる。保持器１９，２０を、鉄板保持器（金属板を打ち抜いて形成されたもの）としてもよい。金属板としては、冷間圧延鋼板（ＳＰＣ）や熱間圧延軟鋼板（ＳＰＨ）等の圧延鋼板、及びばね鋼等を使用することができる。また、冷間圧延鋼板（ＳＰＣ）や熱間圧延軟鋼板（ＳＰＨ）であれば、その表面に浸炭窒化処理やガス軟窒化処理等の表面硬化処理を施すのが好ましい。保持器１９、２０を鉄板製とすることによって、保持器の剛性を高めることができ、長期に亘って安定してボール２７，２８を保持することができる。しかも、耐油性に優れ、油への浸漬による材質劣化を防止できる。なお、このタンデム型複列アンギュラ玉軸受は、低トルク化を達成できるものであるので、種々の機械、装置、工具等に使用することができる。   As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications are possible. For example, the number of balls 27 and 28 of the ball groups 15 and 16 and the ball diameter Etc. can be arbitrarily changed as long as they have the same spherical diameter. The cages 19 and 20 may be iron plate cages (formed by punching a metal plate). As the metal plate, rolled steel plate such as cold rolled steel plate (SPC) and hot rolled mild steel plate (SPH), spring steel, and the like can be used. In the case of a cold rolled steel plate (SPC) or a hot rolled mild steel plate (SPH), it is preferable to subject the surface to surface hardening treatment such as carbonitriding treatment or gas soft nitriding treatment. By making the cages 19 and 20 made of iron plate, the rigidity of the cage can be increased, and the balls 27 and 28 can be stably held over a long period of time. Moreover, it is excellent in oil resistance and can prevent material deterioration due to immersion in oil. The tandem double-row angular contact ball bearing can achieve low torque, and can be used for various machines, devices, tools, and the like.

本発明の実施形態を示すタンデム型複列アンギュラ玉軸受の要部拡大断面図である。It is a principal part expanded sectional view of the tandem type double row angular contact ball bearing which shows the embodiment of the present invention. 前記タンデム型複列アンギュラ玉軸受の要部断面図である。It is principal part sectional drawing of the said tandem type double row angular contact ball bearing. 従来のタンデム型複列アンギュラ玉軸受の断面図である。It is sectional drawing of the conventional tandem type double row angular contact ball bearing.

符号の説明Explanation of symbols

１１ａ 軌道面
１１ｂ 軌道面
１２ 内輪
１３ａ 軌道面
１３ｂ 軌道面
１４ 外輪
１５ 玉群
１６ 玉群
１９ 保持器
２０ 保持器
２７ ボール
２８ ボール 11 a raceway surface 11 b raceway surface 12 inner ring 13 a raceway surface 13 b raceway surface 14 outer ring 15 ball group 16 ball group 19 cage 20 cage 27 ball 28 ball

Claims (3)

複列の軌道面を有する内輪と、この内輪の軌道面と対応する複列の軌道面を有する外輪と、内輪および外輪の各列の軌道面間に、それぞれ異なるピッチ円直径をもって介装される複列の玉群とを備えたタンデム型複列アンギュラ玉軸受において、
大径側のボール接触角と小径側のボール接触角とを相違させて、大径側のボールと小径側のボールとの公転回転数の差を１０％以下に設定したことを特徴とするタンデム型複列アンギュラ玉軸受。 An inner ring having a double-row raceway surface, an outer ring having a double-row raceway surface corresponding to the raceway surface of the inner ring, and a raceway surface in each row of the inner ring and the outer ring are interposed with different pitch circle diameters. In tandem double row angular contact ball bearings with double row balls,
The tandem is characterized in that the difference in revolution speed between the large-diameter side ball and the small-diameter side ball is set to 10% or less by making the large-diameter side ball contact angle different from the small-diameter side ball contact angle. Type double row angular contact ball bearing. 大径側のボール保持器と小径側のボール保持器とを接触させたことを特徴とする請求項１のタンデム型複列アンギュラ玉軸受。   2. The tandem double-row angular ball bearing according to claim 1, wherein the large-diameter side ball cage and the small-diameter side ball cage are brought into contact with each other. 大径側のボール保持器と小径側のボール保持器とを一体化したことを特徴とする請求項１のタンデム型複列アンギュラ玉軸受。   2. The tandem double-row angular contact ball bearing according to claim 1, wherein the large-diameter side ball cage and the small-diameter side ball cage are integrated.
JP2006328420A 2006-12-05 2006-12-05 Tandem type double row angular contact ball bearing Expired - Fee Related JP4722822B2 (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008240769A (en) * 2007-03-26 2008-10-09 Jtekt Corp Double-row ball bearing
WO2011062175A1 (en) * 2009-11-19 2011-05-26 Ntn株式会社 Bearing device for wheels
WO2011062257A1 (en) * 2009-11-20 2011-05-26 日本精工株式会社 Tandem angular type ball bearing
JP2011106633A (en) * 2009-11-20 2011-06-02 Nsk Ltd Tandem type double row angular contact ball bearing
JP2011106649A (en) * 2009-11-20 2011-06-02 Nsk Ltd Tandem angular contact ball bearing
DE102013203981A1 (en) * 2013-03-08 2014-09-11 Aktiebolaget Skf Double row angular contact ball bearing

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003329043A (en) * 2002-05-10 2003-11-19 Ina Schaeffler Kg Double row angular ball bearings
JP2004124996A (en) * 2002-09-30 2004-04-22 Koyo Seiko Co Ltd Assembly for double-row ball bearing
WO2005088144A1 (en) * 2004-03-11 2005-09-22 Jtekt Corporation Skew contact double row ball bearing and bearing device for supporting pinion shaft

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003329043A (en) * 2002-05-10 2003-11-19 Ina Schaeffler Kg Double row angular ball bearings
JP2004124996A (en) * 2002-09-30 2004-04-22 Koyo Seiko Co Ltd Assembly for double-row ball bearing
WO2005088144A1 (en) * 2004-03-11 2005-09-22 Jtekt Corporation Skew contact double row ball bearing and bearing device for supporting pinion shaft

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008240769A (en) * 2007-03-26 2008-10-09 Jtekt Corp Double-row ball bearing
WO2011062175A1 (en) * 2009-11-19 2011-05-26 Ntn株式会社 Bearing device for wheels
WO2011062257A1 (en) * 2009-11-20 2011-05-26 日本精工株式会社 Tandem angular type ball bearing
JP2011106633A (en) * 2009-11-20 2011-06-02 Nsk Ltd Tandem type double row angular contact ball bearing
JP2011106649A (en) * 2009-11-20 2011-06-02 Nsk Ltd Tandem angular contact ball bearing
DE102013203981A1 (en) * 2013-03-08 2014-09-11 Aktiebolaget Skf Double row angular contact ball bearing
DE102013203981B4 (en) * 2013-03-08 2014-12-24 Aktiebolaget Skf Double row angular contact ball bearing

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