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JP2008169870A - Tandem type double row angular ball bearing and differential device - Google Patents

Tandem type double row angular ball bearing and differential device Download PDF

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Publication number
JP2008169870A
JP2008169870A JP2007001446A JP2007001446A JP2008169870A JP 2008169870 A JP2008169870 A JP 2008169870A JP 2007001446 A JP2007001446 A JP 2007001446A JP 2007001446 A JP2007001446 A JP 2007001446A JP 2008169870 A JP2008169870 A JP 2008169870A
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double
row
ball bearing
balls
differential
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Japanese (ja)
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Tomoki Matsushita
知樹 松下
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2007001446A priority Critical patent/JP2008169870A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling 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
    • F16C33/38—Ball cages
    • F16C33/40—Ball cages for multiple rows of balls
    • F16C33/405—Ball cages for multiple rows of balls with two or more juxtaposed cages joined together or interacting with each other
    • 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]
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tandem type double row angular ball bearing having a longer life and lower differential torque for improving fuel economy by increasing the filling rate of balls to increase a rated load while maintaining the strength of cages. <P>SOLUTION: The tandem type double-row angular ball bearing comprises an inner ring 12 having double-row raceway surfaces 11a, 11b, an outer ring 14 having double-row raceway surfaces 13a, 13b corresponding to the raceway surfaces 11a, 11b of the inner ring 12, double-row ball groups 15, 16 having different pitch circle diameters and mounted between the double-row raceway surfaces of the inner ring 12 and the outer ring 14, and the cages 19, 20 for holding the balls 27, 28 of the ball groups 15, 16. The filling rate of the balls 27, 28 represented by ä(ball diameter×ball number÷(π×pitch circle diameter))×100(%)} is 91% or more in double rows. <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及びデファレンシャル装置に関する。   The present invention relates to a tandem type double row angular contact ball bearing and a differential device.

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. The ball and the inner ring / outer ring have a contact angle. The larger the contact angle, the greater the load capacity of the axial load, and 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。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１）。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 a tapered roller bearing. In addition, there is one in which this tandem type double row angular ball bearing is used for an automobile transfer (Patent Document 1). 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 into one body, so that it can load an axial load in both directions, and has a load capacity for moment load. 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。   As shown in FIG. 3, the tandem type double-row angular 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 double-row ball groups 5 and 6 interposed between the raceways 1a, 1b, 3a and 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 the ball groups 5 and 6 are held by cages 9 and 10 disposed between the inner ring 2 and the outer ring 4.

前記特許文献１に記載のデファレンシャル装置は、図４に示すように、デファレンシャルケース１０１と、このデファレンシャルケース１０１内に配置される差動減速機構（図外）と、差動減速機構のリングギヤ（図外）に噛合するピニオンギヤ１０４と、ピニオンギヤ１０４を支持するピニオン軸１０５とを備え、ピニオン軸１０５が軸受１０６、１０７を介して回転自在にデファレンシャルケース１０１内に支持されている。   As shown in FIG. 4, the differential device described in Patent Document 1 includes a differential case 101, a differential reduction mechanism (not shown) disposed in the differential case 101, and a ring gear (see FIG. And a pinion shaft 105 that supports the pinion gear 104. The pinion shaft 105 is rotatably supported in the differential case 101 via bearings 106 and 107.

そして、軸受１０６、１０７にそれぞれタンデム型複列アンギュラ玉軸受を使用している。ピニオンギヤ１０４側に配設される一方の軸受１０６は、内輪２の大径側端面２ａ（外輪４よりもピニオンギヤ１０４側に突出している端面）がピニオンギヤ１０４の端面１０４ａに圧接するとともに、外輪４の反ピニオンギヤ側の端面４ａがケース１０１の内面に形成された段差面１０８に圧接している。   And tandem type double row angular contact ball bearings are used for the bearings 106 and 107, respectively. One bearing 106 disposed on the pinion gear 104 side has a large-diameter side end surface 2a of the inner ring 2 (an end surface protruding to the pinion gear 104 side from the outer ring 4) press-contacts the end surface 104a of the pinion gear 104, and The end surface 4 a on the side opposite to the pinion gear is in pressure contact with a step surface 108 formed on the inner surface of the case 101.

他方の軸受１０７は、内輪２の大径側端面２ａ（外輪４よりも反ピニオンギヤ側に突出している端面）がピニオンフランジ１００の端縁１００ａに圧接するとともに、外輪４のピニオンギヤ側の端面４ａがケース１０１の内面に形成された段差面１０９に圧接している。また、ピニオン軸１０５は、そのピニオンギヤ１０４側は大径とされて段差部１０５ａが形成され、この段差部１０５ａと他方の軸受１０７の内輪２との間にスリーブ１１０が介在されている。   The other bearing 107 has a large-diameter side end surface 2a of the inner ring 2 (an end surface protruding to the side opposite to the pinion gear from the outer ring 4) press-contacts the end edge 100a of the pinion flange 100, and an end surface 4a of the outer ring 4 on the pinion gear side. The step 101 is in pressure contact with the step surface 109 formed on the inner surface of the case 101. Further, the pinion shaft 105 has a large diameter on the pinion gear 104 side to form a stepped portion 105a, and a sleeve 110 is interposed between the stepped portion 105a and the inner ring 2 of the other bearing 107.

この場合、ピニオン軸１０５の端部のねじ部１１１にナット部材（図示省略）を螺合することによって、ピニオンフランジ１００を介して軸受１０６、１０７に予圧を付与することになる。すなわち、軸受１０６、１０７に予圧を付与することによって、軸受支持構造の剛性が増し、ピニオン軸１０５の位置が安定してリングギヤとの噛み合いが良好となる。   In this case, a preload is applied to the bearings 106 and 107 via the pinion flange 100 by screwing a nut member (not shown) to the threaded portion 111 at the end of the pinion shaft 105. That is, by applying preload to the bearings 106 and 107, the rigidity of the bearing support structure is increased, the position of the pinion shaft 105 is stabilized, and the meshing with the ring gear is improved.

ところで、近年、自動車では省エネルギー及び環境問題の観点から、車両の低燃費化が要求されている。低燃費化のためには、軸受には起動トルク、回転トルクの低減が求められる。デファレンシャル装置においては、高粘土の油が用いられるため、軸受の回転トルクは大きく、また、大きな荷重を受けるため、そこに使われる軸受は従来円すいころ軸受が用いられてきた。これにより、デファレンシャル装置でのエネルギー損失は大きかった。
特表２００２−５２３７１０号 Incidentally, in recent years, automobiles have been required to reduce the fuel consumption of vehicles from the viewpoint of energy saving and environmental problems. In order to reduce fuel consumption, the bearings are required to reduce starting torque and rotational torque. In the differential apparatus, since high clay oil is used, the rotational torque of the bearing is large, and since a large load is received, a tapered roller bearing has been conventionally used. As a result, the energy loss in the differential device was large.
Special table 2002-523710

そこで、トルクを低減するために、前記特許文献１に記載のように、軸受を円すいころ軸受からアンギュラ玉軸受を用いることが考えられる。しかし、アンギュラ玉軸受に変更することで、定格荷重が下がるため、必要寿命を満足することができない。必要寿命を満足するためには、ボールの充填率を上げて、定格荷重を上げる必要がある。ところが、現在のアンギュラ玉軸受の保持器形式は様々な形状があり、ボールの充填率は、平均で８０％であった。   Therefore, in order to reduce torque, it is conceivable to use an angular ball bearing instead of a tapered roller bearing as described in Patent Document 1. However, by changing to an angular ball bearing, the rated load is lowered, so the required life cannot be satisfied. In order to satisfy the required life, it is necessary to increase the filling rate of the balls and increase the rated load. However, the cage type of the present angular ball bearing has various shapes, and the filling rate of balls is 80% on average.

本発明は、上記課題に鑑みて、保持器の強度を保ちつつボールの充填率を上げることができ、定格荷重を上げることができて、軸受の長寿命化を図ることができるとともに、デファレンシャルにおける軸受の低トルク化により低燃費化を図ることができるデファレンシャル装置およびこのデファレンシャル装置に好適に用いることができる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 can increase the filling rate of balls while maintaining the strength of the cage, can increase the rated load, and can extend the life of the bearing. Provided are a differential device capable of reducing fuel consumption by reducing the torque of the bearing, and a tandem double-row angular ball bearing that can be suitably used for the differential device.

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、前記玉群のボールを保持する保持器とを備えたタンデム型複列アンギュラ玉軸受において、｛（ボール径×ボール個数÷（π×ピッチ円直径））×１００（％）｝で表されるボールの充填率を複列毎に９１％以上としたものである。   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 a tandem double row angular contact ball bearing having a double row ball group interposed with different pitch circle diameters and a cage for holding the balls of the ball group, {(ball diameter × number of balls ÷ (Π × pitch circle diameter)) × 100 (%)} is set to 91% or more for each double row.

本発明のタンデム型複列アンギュラ玉軸受によれば、タンデム型複列アンギュラ玉軸受において、ボールの充填率を９１％以上としたので、限られたスペース内でボールの充填率を上げることができ、定格荷重を上げることができる。   According to the tandem double-row angular contact ball bearing of the present invention, in the tandem double-row angular contact ball bearing, since the ball filling rate is 91% or more, the ball filling rate can be increased in a limited space. The rated load can be increased.

前記保持器が、幅方向中央にポケットを有する窓型とすることができる。これにより、保持器の強度を保ちつつ、ボールの充填率を上げることができて、定格荷重を上げることができる。   The cage may be a window type having a pocket in the center in the width direction. As a result, the ball filling rate can be increased while maintaining the strength of the cage, and the rated load can be increased.

本発明のデファレンシャル装置は、デファレンシャルケースと、このデファレンシャルケース内に配置される差動減速機構と、差動減速機構のリングギヤに噛合するピニオンギヤと、ピニオンギヤを支持するピニオン軸とを備えたデファレンシャル装置であって、前記ピニオン軸が請求項１又は２に記載のタンデム型複列アンギュラ玉軸受にてデファレンシャルケース内に回転自在に支持されるものである。   A differential apparatus of the present invention is a differential apparatus including a differential case, a differential reduction mechanism disposed in the differential case, a pinion gear meshing with a ring gear of the differential reduction mechanism, and a pinion shaft that supports the pinion gear. The pinion shaft is rotatably supported in the differential case by the tandem double-row angular contact ball bearing according to claim 1 or 2.

本発明のデファレンシャル装置によれば、請求項１又は２に記載のタンデム型複列アンギュラ玉軸受にてデファレンシャルケース内に回転自在に支持される。   According to the differential device of the present invention, the tandem double-row angular contact ball bearing according to claim 1 or 2 is rotatably supported in the differential case.

本発明のタンデム型複列アンギュラ玉軸受では、保持器の強度を保ちつつ、ボールの充填率を上げることができる（すなわち、窓型保持器を用いることで従来達成できなかった、保持器強度を確保したまま充填率９１％を達成することが出来る）ため、定格荷重を上げることができて、軸受の長寿命化を図ることができる。   In the tandem double-row angular contact ball bearing of the present invention, the filling rate of the balls can be increased while maintaining the strength of the cage (that is, the cage strength that could not be achieved conventionally by using a window-type cage). (The filling rate can be 91% while ensuring), so the rated load can be increased and the life of the bearing can be extended.

本発明のデファレンシャル装置では、請求項１又は２に記載のタンデム型複列アンギュラ玉軸受にてデファレンシャルケース内に回転自在に支持されるため、軸受の長寿命化を図ることができ、デファレンシャルにおける軸受の低トルク化により低燃費化を図ることができる。これにより、自動車の燃費改善の一躍を担うことができる。   In the differential device of the present invention, the bearing is rotatably supported in the differential case by the tandem double-row angular contact ball bearing according to claim 1 or 2, so that the life of the bearing can be extended. Lowering the torque can reduce fuel consumption. As a result, it is possible to take a leap forward in improving the fuel efficiency of automobiles.

以下本発明の実施の形態を図１及び図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に本発明のタンデム型アンギュラ玉軸受を示し、このタンデム型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。   FIG. 1 shows a tandem type angular contact ball bearing of the present invention. This tandem type angular contact ball bearing has an inner ring 12 having double row raceway surfaces 11a and 11b, and a double row corresponding to the raceway surfaces 11a and 11b of the inner ring 12. The outer race 14 having the raceway surfaces 13a and 13b and the double row ball groups 15 and 16 interposed between the raceways 11a, 11b, 13a and 13b of the inner race 12 and the outer race 14 in each row.

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。   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.

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はそれぞれ保持器１９、２０にて保持される。保持器１９、２０は、テーパ筒形のリング状に形成した合成樹脂製のものであって、ボール２７、２８の保持用の複数のポケット３２を、軸方向幅の中間部で周方向に多数並べて設けた窓型のものとしてある。保持器１９、２０の各ポケット３２、３２間の部分は、傾斜した柱状の仕切り壁３４となり、ポケット３２よりも小径側の部分および大径側の部分は、各々内径面および外径面が共に円筒面状となった小径円環部３０および大径円環部３１となっている。各仕切り壁３４の両側面は、ボール２７、２８の外径に応じた球面状としてある。   The ball groups 15 and 16 are held by holders 19 and 20, respectively. The cages 19 and 20 are made of a synthetic resin formed in a tapered cylindrical ring shape, and a plurality of pockets 32 for holding the balls 27 and 28 are arranged in the circumferential direction at an intermediate portion of the axial width. The windows are arranged side by side. A portion between the pockets 32 and 32 of the cages 19 and 20 is an inclined columnar partition wall 34, and a portion on the smaller diameter side and a portion on the larger diameter side of the pocket 32 have both inner and outer diameter surfaces. A small-diameter annular portion 30 and a large-diameter annular portion 31 are formed in a cylindrical surface shape. Both side surfaces of each partition wall 34 have a spherical shape corresponding to the outer diameters of the balls 27 and 28.

ところで、この軸受のボール２７、２８の充填率を９１％以上としている。ここで、充填率とは、｛（ボール径×ボール個数÷（π×ピッチ円直径））×１００（％）｝で表されるボール複列毎の充填率をいう。   By the way, the filling rate of the balls 27 and 28 of this bearing is set to 91% or more. Here, the filling rate means a filling rate for each double row of balls represented by {(ball diameter × number of balls ÷ (π × pitch circle diameter)) × 100 (%)}.

本発明では、タンデム型複列アンギュラ玉軸受において、ボール２７、２８の充填率を９１％以上としたので、限られたスペース内でボール２７、２８の充填率を上げることができ、定格荷重を上げることができて、軸受の長寿命化を図ることができる。なお、９１％未満であると、定格荷重を上げることができず、軸受の長寿命化を図ることができない。   In the present invention, in the tandem type double row angular contact ball bearing, since the filling rate of the balls 27 and 28 is 91% or more, the filling rate of the balls 27 and 28 can be increased in a limited space, and the rated load can be increased. This can increase the life of the bearing. If it is less than 91%, the rated load cannot be increased and the life of the bearing cannot be extended.

前記保持器１９、２０を、幅方向中央にポケット３２を有する窓型としている。これにより、保持器１９、２０の強度を保ちつつ、ボール２７、２８の充填率を上げることができる。すなわち、窓型保持器を用いることで従来達成できなかった、保持器強度を確保したまま充填率９１％を達成することが出来る。従って、定格荷重を上げることができて、軸受の長寿命化を図ることができる。   The cages 19 and 20 have a window shape having a pocket 32 at the center in the width direction. Thereby, the filling rate of the balls 27 and 28 can be increased while maintaining the strength of the cages 19 and 20. That is, by using a window type cage, a filling rate of 91% can be achieved while securing the cage strength, which could not be achieved conventionally. Therefore, the rated load can be increased and the life of the bearing can be extended.

次に、図２は本発明にかかるタンデム型複列アンギュラ玉軸受を使用したデファレンシャル装置を示し、このデファレンシャル装置は、デファレンシャルケース５１と、このデファレンシャルケース５１内に配置される差動減速機構５２と、差動減速機構５２のリングギヤ５３に噛合するピニオンギヤ５４と、ピニオンギヤ５４を支持するピニオン軸５５とを備え、ピニオン軸５５が軸受５６、５７を介して回転自在にデファレンシャルケース５１内に支持されている。   Next, FIG. 2 shows a differential device using a tandem type double-row angular ball bearing according to the present invention. This differential device includes a differential case 51 and a differential reduction mechanism 52 disposed in the differential case 51. The pinion gear 54 meshes with the ring gear 53 of the differential reduction mechanism 52 and the pinion shaft 55 that supports the pinion gear 54. The pinion shaft 55 is rotatably supported in the differential case 51 via bearings 56 and 57. Yes.

そして、軸受５６、５７にそれぞれ前記図１に示すタンデム型複列アンギュラ玉軸受を使用している。ピニオンギヤ５４側に配設される一方の軸受５６は、ピニオン軸５５のピニオンギヤ５４の端面５４aに軸受５６の内輪１２の端部３３、つまり端面１２aが圧接するとともに、外輪１４の反ピニオンギヤ側の端面１４ａがケース５１の内面に形成された段差面５８に圧接している。   The tandem double-row angular ball bearings shown in FIG. 1 are used for the bearings 56 and 57, respectively. One of the bearings 56 disposed on the pinion gear 54 side is in contact with the end portion 33 of the inner ring 12 of the bearing 56, that is, the end surface 12a, on the end surface 54a of the pinion gear 54 of the pinion shaft 55, and the end surface of the outer ring 14 on the side opposite to the pinion gear. 14 a is in pressure contact with a step surface 58 formed on the inner surface of the case 51.

他方の軸受５７は、内輪１２の端部３３、つまり端面１２a（反フランジ側の端面）がピニオンフランジ５０の端縁５０aに圧接するとともに、外輪１４のピニオンギヤ側の端面１４ａがケース５１の内面に形成された段差面５９に圧接している。また、一方の軸受５６と他方の軸受５７の内輪１２との間にスリーブ６０が介在されている。   In the other bearing 57, the end portion 33 of the inner ring 12, that is, the end surface 12 a (the end surface on the opposite flange side) is pressed against the end edge 50 a of the pinion flange 50, and the end surface 14 a of the outer ring 14 on the pinion gear side is on the inner surface of the case 51. It is in pressure contact with the formed step surface 59. A sleeve 60 is interposed between the one bearing 56 and the inner ring 12 of the other bearing 57.

この場合、ピニオン軸５５の端部のねじ部６１にナット部材６２を螺合することによって、ピニオンフランジ５０を介して軸受５６、５７に予圧を付与することになる。   In this case, a preload is applied to the bearings 56 and 57 via the pinion flange 50 by screwing the nut member 62 into the threaded portion 61 at the end of the pinion shaft 55.

軸受５６、５７の長寿命化を図ることができ、デファレンシャルにおける軸受５６、５７の低トルク化により低燃費化を図ることができる。これにより、自動車の燃費改善の一躍を担うことができる。   The life of the bearings 56 and 57 can be extended, and the fuel consumption can be reduced by reducing the torque of the bearings 56 and 57 in the differential. As a result, it is possible to take a leap forward in improving the fuel efficiency of automobiles.

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、このタンデム型複列アンギュラ玉軸受は、転がり抵抗を低減することができるものであるので、デファレンシャル装置以外の種々の機械、装置、工具等に使用することができる。また、玉群１５，１６のボール２７、２８の数、球径等は任意に変更できる。なお、図２に示すデファレンシャル装置では、タンデム型複列アンギュラ玉軸受にて構成したが、どちらか一方の軸受５６，５７が、タンデム型複列アンギュラ玉軸受ではなくて円すいころ軸受であってもよい。   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 can be made. For example, this tandem double-row angular ball bearing reduces rolling resistance. Therefore, it can be used for various machines, devices, tools and the like other than the differential device. Further, the number of balls 27 and 28 of the ball groups 15 and 16, the diameter of the sphere, and the like can be arbitrarily changed. In the differential device shown in FIG. 2, the tandem double-row angular contact ball bearing is configured. However, either one of the bearings 56 and 57 is not a tandem double-row angular contact ball bearing but a tapered roller bearing. Good.

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断面図である。It is sectional drawing of the tandem type | mold double row angular contact ball bearing which shows embodiment of this invention. 本発明の実施形態を示すデファレンシャル装置の断面図である。It is sectional drawing of the differential apparatus which shows embodiment of this invention. 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. 従来のデファレンシャル装置の断面図である。It is sectional drawing of the conventional differential apparatus.

符号の説明Explanation of symbols

１１ａ、１１ｂ 軌道面
１２ 内輪
１３ａ、１３ｂ 軌道面
１４ 外輪
１５、１６ 玉群
１９、２０ 保持器
２７、２８ ボール 11a, 11b Raceway surface 12 Inner ring 13a, 13b Raceway surface 14 Outer ring 15, 16 Ball group 19, 20 Cage 27, 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、前記玉群のボールを保持する保持器とを備えたタンデム型複列アンギュラ玉軸受において、
｛（ボール径×ボール個数÷（π×ピッチ円直径））×１００（％）｝で表されるボールの充填率を複列毎に９１％以上と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 a tandem double-row angular contact ball bearing comprising a double-row ball group and a cage for holding the balls of the ball group,
Tandem-type double-row angular contact characterized in that the filling ratio of balls represented by {(ball diameter × number of balls ÷ (π × pitch circle diameter)) × 100 (%)} is 91% or more for each double-row. Ball bearing. 前記保持器が、幅方向中央にポケットを有する窓型である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 cage is a window type having a pocket in the center in the width direction. デファレンシャルケースと、このデファレンシャルケース内に配置される差動減速機構と、差動減速機構のリングギヤに噛合するピニオンギヤと、ピニオンギヤを支持するピニオン軸とを備えたデファレンシャル装置であって、
前記ピニオン軸が前記請求項１又は２に記載のタンデム型複列アンギュラ玉軸受にてデファレンシャルケース内に回転自在に支持されることを特徴とするデファレンシャル装置。 A differential device comprising a differential case, a differential reduction mechanism disposed in the differential case, a pinion gear meshing with a ring gear of the differential reduction mechanism, and a pinion shaft that supports the pinion gear,
3. A differential apparatus, wherein the pinion shaft is rotatably supported in a differential case by the tandem double-row angular ball bearing according to claim 1 or 2.
JP2007001446A 2007-01-09 2007-01-09 Tandem type double row angular ball bearing and differential device Pending JP2008169870A (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0478331A (en) * 1990-07-18 1992-03-12 Aisin Chem Co Ltd Finishing of friction material and friction material
JPH0814258A (en) * 1994-06-28 1996-01-16 Ntn Corp Bearing holder and bearing
JPH09236127A (en) * 1996-02-29 1997-09-09 Ntn Corp Resin cage for angular ball bearing
JP2006022824A (en) * 2004-07-05 2006-01-26 Ntn Corp Tapered roller bearing for differential
JP2006038020A (en) * 2004-07-23 2006-02-09 Koyo Seiko Co Ltd Rolling bearing device and double raw ball bearing to be used for the same

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0478331A (en) * 1990-07-18 1992-03-12 Aisin Chem Co Ltd Finishing of friction material and friction material
JPH0814258A (en) * 1994-06-28 1996-01-16 Ntn Corp Bearing holder and bearing
JPH09236127A (en) * 1996-02-29 1997-09-09 Ntn Corp Resin cage for angular ball bearing
JP2006022824A (en) * 2004-07-05 2006-01-26 Ntn Corp Tapered roller bearing for differential
JP2006038020A (en) * 2004-07-23 2006-02-09 Koyo Seiko Co Ltd Rolling bearing device and double raw ball bearing to be used for the same

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