JP2008169921A - 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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JP2008169921A
JP2008169921A JP2007003622A JP2007003622A JP2008169921A JP 2008169921 A JP2008169921 A JP 2008169921A JP 2007003622 A JP2007003622 A JP 2007003622A JP 2007003622 A JP2007003622 A JP 2007003622A JP 2008169921 A JP2008169921 A JP 2008169921A
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double
row
ball bearing
differential
row angular
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Yasuhiro Uehori
泰裕 上堀
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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
    • 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
    • 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)
  • General Details Of Gearings (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tandem type double-row angular ball bearing having a cage capable of preventing degradation of strength even if it is used in oil containing large amounts of phosphorous and sulfur contents, and also to provide a differential device using the tandem type double-row angular ball bearing. <P>SOLUTION: This tandem type double-row angular ball bearing is provided with: an inner ring 12 having double-row raceway surfaces 11a and 11b; an outer ring 14 having double-row raceway surfaces 13a and 13b corresponding to the raceway surfaces 11a and 11b of the inner ring 12; and double-row ball groups 15 and 16 respectively interposed between the raceway surfaces 11a, 11b, 13a and 13b of the respective rows of the inner ring 12 and the outer ring 14, and having pitch circle diameters different from each other. The cages 19 holding balls 27 and 28 of the respective ball groups 15 and 16 are formed of high-strength brass, and pockets 32 for housing the balls 27 and 28 therein are finished by broaching. <P>COPYRIGHT: (C)2008,JPO&amp;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（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 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４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. 4, 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 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２に記載のデファレンシャル装置は、図５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. 5, the differential device described in Patent Document 2 includes a differential case 101, a differential reduction mechanism (not shown) arranged 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。
特許第１８１５４７号 特開２００４−１８３７４５号公報 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.
Patent No. 181547 JP 2004-183745 A

ところで、軸受の保持器は、転動体が軸受から外れることを防ぐとともに、転動体を軸受の中で等間隔に保持して転動体同士の接触を防ぎ、高速回転を助ける役割を持っている。また、保持器には、打抜き保持器（プレス加工で造った保持器）、もみ抜き保持器（削り加工で造った保持器）などがあり、さらには、プラスチックを使用した成形保持器（樹脂保持器）もある。   Incidentally, the cage of the bearing has a role of preventing high speed rotation while preventing the rolling elements from coming off the bearing and holding the rolling elements at equal intervals in the bearing to prevent contact between the rolling elements. In addition, the cage includes punching cages (cage made by pressing), machined cages (cage made by machining), and plastic molded cages (resin holding). There is also a container.

そして、前記特許文献２に記載のデファレンシャル装置における軸受の保持器には、樹脂保持器が使用されている。樹脂保持器は射出成型により大量生産が可能である。このため、近年多く利用されている。しかしながら、デファレンシャル装置に使用される油（デファレンシャル油）は、リン（Ｐ）や硫黄（Ｓ）分が含まれている。このため、デファレンシャル油中で、樹脂保持器が使用されると、樹脂材にＰやＳが浸入して、強度低下を招くおそれがあった。   A resin cage is used as a bearing cage in the differential device described in Patent Document 2. The resin holder can be mass-produced by injection molding. For this reason, it has been widely used in recent years. However, the oil (differential oil) used for the differential device contains phosphorus (P) and sulfur (S). For this reason, when a resin retainer is used in differential oil, P or S may enter the resin material, which may cause a decrease in strength.

本発明は、上記課題に鑑みて、リンや硫黄分が多く含まれている油中に使用しても強度の低下を防止できる保持器を備えたタンデム型複列アンギュラ玉軸受およびこのタンデム型複列アンギュラ玉軸受を用いたデファレンシャル装置を提供する。   In view of the above problems, the present invention provides a tandem double-row angular contact ball bearing having a cage that can prevent a decrease in strength even when used in oil that contains a large amount of phosphorus and sulfur, and the tandem-type double ball bearing. A differential device using a row angular contact ball bearing is provided.

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、各玉群のボールを保持する保持器を高力黄銅にて構成するとともに、ボールが収容されるポケットをブローチ加工にて仕上げたものである。ここで、高力黄銅とは、銅を主成分とする合金であり、ＪＩＳ Ｈ５１２０、Ｈ３２５０による。 また、ブローチ加工とは、工作物の下孔に挿入されたブローチが下方向に引き抜かれ、ブローチ下方の荒刃から上方の仕上げ刃へと工作物を少しずつ切削しながら、孔部を所定寸法に仕上げる加工である。   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. In addition, in the tandem double-row angular contact ball bearing provided with the double-row ball group interposed with different pitch circle diameters, the cage for holding the ball of each ball group is made of high-strength brass, The pocket that contains the ball is finished by broaching. Here, high-strength brass is an alloy containing copper as a main component and conforms to JIS H5120 and H3250. Broaching means that the broach inserted into the lower hole of the workpiece is pulled downward, and the hole is cut to a predetermined size while gradually cutting the workpiece from the rough blade below the broach to the upper finishing blade. It is processing to finish.

本発明のタンデム型複列アンギュラ玉軸受によれば、保持器を高力黄銅にて構成しているので、リンや硫黄分が多く含まれている油中に使用してもリンや硫黄が保持器に浸入することがない。しかも、ポケットをブローチ加工にて仕上げたものであり、一工程で仕上げ加工まで行える。   According to the tandem double-row angular contact ball bearing of the present invention, since the cage is made of high-strength brass, phosphorus and sulfur are retained even when used in oils rich in phosphorus and sulfur. It does not enter the vessel. In addition, the pockets are finished by broaching and can be finished in one step.

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、前記ピニオン軸が前記本発明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ているものである。   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 ball bearing of the present invention.

本発明のデファレンシャル装置によれば、軸受の保持器を高力黄銅にて構成しているので、デファレンシャル油に含まれているリンや硫黄が保持器に浸入することがない。このため、この軸受の保持器のポケットをブローチ加工にて仕上げたものであり、一工程で仕上げ加工まで行える。   According to the differential device of the present invention, since the bearing cage is made of high-strength brass, phosphorus and sulfur contained in the differential oil do not enter the cage. For this reason, the pocket of the cage of this bearing is finished by broaching, and finishing can be done in one step.

本発明のタンデム型複列アンギュラ玉軸受では、リンや硫黄分が多く含まれている油中に使用しても強度が低下することがなく、耐久性に優れる。すなわち、保持器は、強さ、硬さが高く、耐食性およびじん性に優れる。このため、ボールを安定して保持することができて、円滑な転動を維持することができ、高品質のタンデム型複列アンギュラ玉軸受を提供できる。また、ブローチ加工は一工程で仕上げ加工まで行えるため生産性が高く、かつ工具の耐久性も予測しやすい。このため大量生産に適し、コスト低減を達成できる。   The tandem type double-row angular contact ball bearing of the present invention is excellent in durability without being reduced in strength even when used in oil containing a large amount of phosphorus and sulfur. That is, the cage is high in strength and hardness, and excellent in corrosion resistance and toughness. For this reason, the ball can be stably held, smooth rolling can be maintained, and a high-quality tandem double-row angular contact ball bearing can be provided. In addition, broaching can be finished in one step, so productivity is high and tool durability is easy to predict. Therefore, it is suitable for mass production and can achieve cost reduction.

本発明のデファレンシャル装置では、デファレンシャル油に対してもタンデム型複列アンギュラ玉軸受の保持器の強度が低下せず、長期にわたってピニオン軸がデファレンシャルケース内で回転自在に安定した状態で支持される。しかも、タンデム型複列アンギュラ玉軸受は、円すいころ軸受に比べて転がり抵抗を低減させることができるので、高品質なデファレンシャル装置を提供できる。また、保持器のポケットをブローチ加工にて仕上げできるので、生産性に優れ、大量生産に適し、コスト低減を達成できる。   In the differential device of the present invention, the strength of the retainer of the tandem double-row angular ball bearing does not decrease even with the differential oil, and the pinion shaft is supported in a stable and freely rotatable manner in the differential case for a long period of time. In addition, since the tandem double-row angular contact ball bearing can reduce rolling resistance as compared with the tapered roller bearing, a high-quality differential device can be provided. Moreover, since the cage pocket can be finished by broaching, it is excellent in productivity, suitable for mass production, and can achieve cost reduction.

以下本発明の実施の形態を図１〜図３に基づいて説明する。   Embodiments of the present invention will be described below 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直径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 and 16 have different pitch circle diameters D1 and D2, respectively. 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切欠部逆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. The end of the first notch 21 opposite to the second notch is the track surface 11a, and the second notch 22 is the track 11b. Further, a circumferential groove 23 is formed on the second notch 22 side of the first notch 21.

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切欠部逆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 opposite to the second notch is the track surface 13b, and the second notch 25 is the track 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は高力黄銅にて構成される。高力黄銅とは、銅を主成分とする合金である。すなわち、保持器１９、２０は、ＪＩＳのＨ５１０２，Ｈ３２５０に規定されているＨＢｓＣｌ（ＣＡＣ３０１）、Ｃ６７８２のような高力黄銅，またはこれらの改良材料などが使用可能である。ここで、ＨＢｓＣ１は、Ｃｕを５５．０％以上、Ｍｎを１．５％以下、Ｆｅを０．５〜１．５％、Ａｌを０．５〜１．５％、Ｓｎを１．０％以下、Ｎｉを１．０％以下、不純物としてＰｂを０．４以下、Ｓｉを０．１以下含み、残部をＺｎが占める。一方、Ｃ６７８２は、Ｃｕを５６．０〜６０．５％、Ｍｎを０．５〜２．５％、Ｆｅを０．１〜１．０％、Ａｌを０．２〜２．０％、不純物としてＰｂを０．５以下含み、残部をＺｎが占める。   The ball groups 15 and 16 are held by holders 19 and 20, respectively. The cages 19 and 20 are made of high-strength brass. High-strength brass is an alloy mainly composed of copper. That is, the retainers 19 and 20 can use high strength brass such as HBsCl (CAC301) and C6782 defined in JIS H5102 and H3250, or improved materials thereof. Here, HBsC1 is Cu 55.0% or more, Mn 1.5% or less, Fe 0.5-1.5%, Al 0.5-1.5%, Sn 1.0% Hereinafter, Ni is 1.0% or less, Pb is 0.4 or less as impurities, Si is 0.1 or less, and the balance is Zn. On the other hand, C6782 includes 56.0 to 60.5% Cu, 0.5 to 2.5% Mn, 0.1 to 1.0% Fe, 0.2 to 2.0% Al, impurities As for Pb, 0.5 or less is contained, and the balance is occupied by Zn.

保持器１９、２０はプレス成形にて形成され、平板リング状の基部３０と、この基部３０の外径側から拡径するように延びる周壁３１とを備え、周壁３１に周方向に沿って所定ピッチで配設されるポケット３２が形成されている。各保持器１９、２０のポケット３２には、それぞれ玉群１５、１６を構成するボール２７，２８が保持される。なお、大径側の保持器１９は、その基部３０が内輪１２の周方向溝２３に対応している。   The retainers 19 and 20 are formed by press molding, and include a flat plate ring-shaped base 30 and a peripheral wall 31 extending so as to expand from the outer diameter side of the base 30, and the peripheral wall 31 has a predetermined direction along the circumferential direction. Pockets 32 arranged at a pitch are formed. Balls 27 and 28 constituting ball groups 15 and 16 are held in the pockets 32 of the cages 19 and 20, respectively. Note that the base 30 of the large-diameter side retainer 19 corresponds to the circumferential groove 23 of the inner ring 12.

ポケット３２は、ブローチ加工にて仕上げられる。ここで、ブローチ加工とは、工作物の下孔に挿入されたブローチが下方向に引き抜かれ、ブローチ下方の荒刃から上方の仕上げ刃へと工作物を少しずつ切削しながら、所定寸法に仕上げる加工である。   The pocket 32 is finished by broaching. Here, broaching means that the broach inserted into the lower hole of the workpiece is pulled downward, and the workpiece is finished to a predetermined size while gradually cutting the workpiece from the rough blade below the broach to the upper finishing blade. It is processing.

すなわち、図３に示すように、ブローチ８０とよばれる専用の工具を用いる。ブローチ８０は、棒状の軸部材に、多数の円刃８１が順次寸法（径寸法）を増しながら配列されている工具で、前部に前つかみ部８２、後部に後つかみ部８３があり、その間に荒刃８１ａ、中仕上げ刃８１ｂ、仕上げ刃８１ｃがそれぞれ複数並んでいる。そして、工作物Ｗにガイド孔８４を開け、ブローチ８０の前つかみ部８２を保持して引き抜くと仕上げ刃８１ｃの寸法の孔８５を形成することができる。このように、ブローチ加工は一工程で仕上げ加工まで行えるため生産性が高く、かつ工具の耐久性も予測しやすい。このため大量生産に向いている。   That is, as shown in FIG. 3, a dedicated tool called broach 80 is used. The broach 80 is a tool in which a large number of circular blades 81 are arranged on a rod-shaped shaft member while increasing the size (diameter size) sequentially, and has a front grip portion 82 at the front portion and a rear grip portion 83 at the rear portion. A plurality of rough blades 81a, intermediate finishing blades 81b, and finishing blades 81c are arranged. When the guide hole 84 is opened in the workpiece W and the front gripping portion 82 of the broach 80 is held and pulled out, the hole 85 having the size of the finishing blade 81c can be formed. In this way, broaching can be finished up to one step in a single process, so that productivity is high and tool durability is easy to predict. For this reason, it is suitable for mass production.

本発明では、保持器１９、２０を高力黄銅にて構成しているので、リンや硫黄分が多く含まれている油中に使用してもリンや硫黄が保持器１９、２０に浸入することがない。すなわち、この保持器１９、２０は、強さ、硬さが高く、耐食性およびじん性に優れるものとなる。このため、リンや硫黄分が多く含まれている油中に使用しても強度が低下することがなく、耐久性に優れ、ボール２７、２８を安定して保持することができて、円滑な転動を維持することができ、高品質のタンデム型複列アンギュラ玉軸受を提供できる。しかも、ポケット３２をブローチ加工にて仕上げたものであり、一工程で仕上げ加工まで行える。このため、生産性が高く、かつ工具の耐久性も予測しやすい。このため大量生産に適し、コスト低減を達成できる。   In the present invention, the cages 19 and 20 are made of high-strength brass, so that phosphorus and sulfur enter the cages 19 and 20 even when used in oil containing a large amount of phosphorus and sulfur. There is nothing. That is, the cages 19 and 20 have high strength and hardness, and are excellent in corrosion resistance and toughness. For this reason, even if it is used in oil containing a large amount of phosphorus and sulfur, the strength does not decrease, the durability is excellent, the balls 27 and 28 can be stably held, and smooth. Rolling can be maintained, and a high-quality tandem double-row angular contact ball bearing can be provided. Moreover, the pocket 32 is finished by broaching, and finishing can be done in one step. For this reason, productivity is high and it is easy to predict the durability of the tool. Therefore, it is suitable for mass production and can achieve cost reduction.

次に、図３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. 3 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.

デファレンシャル油に対してもタンデム型複列アンギュラ玉軸受の保持器１９、２０の強度が低下せず、長期にわたってピニオン軸５５がデファレンシャルケース５１内で回転自在に安定した状態で支持される。このため、高品質なデファレンシャル装置を提供できる。しかも、保持器１９，２０のポケット３２をブローチ加工にて仕上げできるので、生産性に優れ、大量生産に適し、コスト低減を達成できる。   The strength of the retainers 19 and 20 of the tandem double-row angular ball bearing does not decrease even with the differential oil, and the pinion shaft 55 is supported in a stable and freely rotatable manner within the differential case 51 for a long period of time. For this reason, a high quality differential apparatus can be provided. Moreover, since the pockets 32 of the cages 19 and 20 can be finished by broaching, it is excellent in productivity, suitable for mass production, and cost reduction can be achieved.

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。さらに、玉群１５、１６の各ピッチ円直径Ｄ１、Ｄ２の差も、使用する機械、装置、工具等に応じて種々変更できる。なお、高力黄銅としては、実施形態において記載したＨＢｓＣｌ（ＣＡＣ３０１）、Ｃ６７８２に限るものではなく、他の種々の高力黄銅をことができる。   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 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. Furthermore, the difference between the pitch circle diameters D1 and D2 of the ball groups 15 and 16 can be variously changed according to the machine, device, tool, and the like to be used. The high-strength brass is not limited to HBsCl (CAC301) and C6782 described in the embodiment, and other various high-strength brass can be used.

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. ブローチ加工の説明図である。It is explanatory drawing of broaching. 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
３２ ポケット
５１ デファレンシャルケース
５２ 差動減速機構
５３ リングギヤ
５４ ピニオンギヤ
５５ ピニオン軸 11a, 11b Raceway surface 12 Inner ring 13a, 13b Raceway surface 14 Outer ring 15, 16 Ball group 19, 20 Cage 27, 28 Ball 32 Pocket 51 Differential case 52 Differential reduction mechanism 53 Ring gear 54 Pinion gear 55 Pinion shaft

Claims (2)

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、
各玉群のボールを保持する保持器を高力黄銅にて構成するとともに、ボールが収容される保持器のポケットをブローチ加工にて仕上げ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,
A tandem double row angular contact ball bearing characterized in that the cage for holding the balls of each ball group is made of high-strength brass and the pocket of the cage in which the balls are accommodated is finished by broaching. 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てい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,
The differential apparatus according to claim 1, wherein the pinion shaft is rotatably supported in a differential case by the tandem double-row angular ball bearing according to claim 1.
JP2007003622A 2007-01-11 2007-01-11 Tandem type double-row angular ball bearing, and differential device Pending JP2008169921A (en)

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001012477A (en) * 1999-04-28 2001-01-16 Nsk Ltd Cage for rolling bearing
JP2004232844A (en) * 2003-02-03 2004-08-19 Koyo Seiko Co Ltd Double row ball bearing

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001012477A (en) * 1999-04-28 2001-01-16 Nsk Ltd Cage for rolling bearing
JP2004232844A (en) * 2003-02-03 2004-08-19 Koyo Seiko Co Ltd Double row ball bearing

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