JP4506160B2 - Bearing device for pinion shaft support - Google Patents

Bearing device for pinion shaft support Download PDF

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JP4506160B2
JP4506160B2 JP2003409272A JP2003409272A JP4506160B2 JP 4506160 B2 JP4506160 B2 JP 4506160B2 JP 2003409272 A JP2003409272 A JP 2003409272A JP 2003409272 A JP2003409272 A JP 2003409272A JP 4506160 B2 JP4506160 B2 JP 4506160B2
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Prior art keywords
outer ring
pinion shaft
pinion gear
case
hole
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JP2005172035A (en
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章之 鈴木
陽三 谷口
健 岩脇
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JTEKT Corp
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JTEKT Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C19/183—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 with two rows at opposite angles
    • F16C19/184—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 with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6666—Details of supply of the liquid to the bearing, e.g. passages or nozzles from an oil bath in the bearing housing, e.g. by an oil ring or centrifugal disc
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • 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
    • 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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
    • F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、ケースにピニオン軸を回転自在に支持するためのピニオン軸支持用軸受装置に関する。このピニオン軸支持用軸受装置は、例えば自動車に備えるトランスファやデファレンシャルなどに用いられる。   The present invention relates to a pinion shaft support bearing device for rotatably supporting a pinion shaft on a case. This pinion shaft support bearing device is used for, for example, a transfer or a differential provided in an automobile.

ピニオン軸支持用軸受装置を複列外向き円すいころ軸受としたものがある（例えば特許文献１参照）。このピニオン軸支持用軸受装置は、軸方向両端をシールなしの開放状態にしていて、トランスファやデファレンシャルなどのケース内部に収容される潤滑油を単一の外輪の軸方向中央の外径側から各円すいころ列の間へ向けて導入し、潤滑油を軸方向両端へ向けて分流させて、各円すいころ列を潤滑している。
特開昭６３−２０７７２５号公報 Some pinion shaft supporting bearing devices are double-row outward tapered roller bearings (see, for example, Patent Document 1). In this pinion shaft support bearing device, both ends in the axial direction are in an open state without a seal, and lubricating oil contained in a case such as a transfer or a differential is transferred from the outer diameter side at the center in the axial direction of a single outer ring. Each tapered roller row is lubricated by introducing it between the tapered roller rows and diverting the lubricating oil toward both ends in the axial direction.
JP-A-63-207725

上記従来例では、軸方向両端をシールなしの開放状態にしているため、軸受内部空間の反ピニオンギヤ側の端部から流れ出た潤滑油を受ける空間を軸受の反ピニオンギヤ側外部に設けるとともに、この空間からの潤滑油の外部漏洩を防止するための密封構造と、前記空間からケース内部へ潤滑油を戻すための通路とを確保する必要があるために、複雑でコストが高く構造となっている。   In the above conventional example, both ends in the axial direction are opened without seals, so that a space for receiving the lubricating oil flowing out from the end on the side opposite to the pinion gear of the bearing inner space is provided outside the bearing on the side opposite to the pinion gear. Since it is necessary to secure a sealing structure for preventing external leakage of the lubricating oil from the inside and a passage for returning the lubricating oil from the space to the inside of the case, the structure is complicated and expensive.

本発明は、一端にピニオンギヤを有するピニオン軸を支持するピニオン軸支持用軸受装置において、単一の外輪と二つの内輪との間に二列の玉を介装した複列外向きアンギュラ玉軸受とされ、その軸受内部空間の反ピニオンギヤ側がシールで閉塞されるとともにピニオンギヤ側が開放され、前記外輪に、外径側から反ピニオンギヤ側の玉列の軌道面よりも端縁側のカウンタボアへ貫通し反ピニオンギヤ側の玉列と前記シールとの間に潤滑油を導入する油孔が設けられていることを特徴としている。 The present invention relates to a pinion shaft support bearing device for supporting a pinion shaft having a pinion gear at one end, and a double row outward angular ball bearing in which two rows of balls are interposed between a single outer ring and two inner rings. The anti-pinion gear side of the bearing internal space is closed with a seal and the pinion gear side is opened, and the outer ring penetrates from the outer diameter side to the counter bore on the edge side of the raceway surface of the ball train on the anti-pinion gear side. An oil hole for introducing lubricating oil is provided between the ball array on the side and the seal.

この場合、軸受内部空間における反ピニオンギヤ側からピニオンギヤ側へ一方向に潤滑油が通過するようになって、十分な潤滑油で各玉列が潤滑される。しかも、軸受内部空間の反ピニオンギヤ側にシールを装着しただけであり、従来例のように複雑な構造を確保する必要がなくなる。   In this case, the lubricating oil passes in one direction from the non-pinion gear side to the pinion gear side in the bearing internal space, and each ball train is lubricated with sufficient lubricating oil. In addition, since a seal is only mounted on the side of the bearing inner space opposite to the pinion gear, it is not necessary to secure a complicated structure as in the conventional example.

前記外輪は、軸方向両端にカウンタボアを有し、前記二つの内輪は、それぞれ軸方向内端にカウンタボアを有し、前記シールは、前記外輪における反ピニオンギヤ側のカウンタボアに取り付けられる胴体部と、この胴体部の内周に設けられかつ前記反ピニオンギヤ側の内輪の肩部に接触するとともに、軸受内側へ向けて開きうるリップとを有したものとすることができる。
また、本願発明に係るピニオン軸支持用軸受装置は、上記のものにおいて、前記ピニオン軸を挿通した状態で支持するための貫通孔を有するケースと、前記貫通孔に設けられ軸方向に沿った溝と、前記外輪の外径面に形成されたフランジと、を備え、前記外輪は、前記ケースの貫通孔に嵌合された状態で、前記フランジが前記ケースにボルト固定され、前記溝によって前記外輪と前記ケースの貫通孔との嵌め合い面に前記油孔に連通する油通路が形成されるものが好ましい。 The outer ring has counter bores at both ends in the axial direction, the two inner rings each have a counter bore at the inner end in the axial direction, and the seal is a body portion attached to the counter bore on the side opposite to the pinion gear in the outer ring. And a lip that is provided on the inner periphery of the body portion and that contacts the shoulder portion of the inner ring on the side opposite to the pinion gear and can open toward the inside of the bearing.
The pinion shaft support bearing device according to the present invention is the above-described bearing device having a through hole for supporting the pinion shaft in a state of being inserted, and a groove provided in the through hole along the axial direction. And a flange formed on the outer diameter surface of the outer ring, and the outer ring is bolted to the case in a state where the outer ring is fitted in a through hole of the case, and the outer ring is formed by the groove. It is preferable that an oil passage communicating with the oil hole is formed on a fitting surface between the case and the through hole of the case.

前記外輪の外径部に当該軸受装置をケースに固定するためのフランジを設け、前記油孔を外輪の外径部であってフランジの根元から外輪の反ピニオンギヤ側のカウンタボアに向けて斜めに貫通させて設けることができる。
ピニオン軸のピニオンギヤをケースの内部に位置させた状態でピニオン軸の胴部を当該軸受装置を介してケースの貫通孔に回転自在に支持させ、ケースの貫通孔の円周方向複数箇所に軸方向に沿う溝を設けるとともに、当該溝によって外輪とケースの貫通孔との嵌め合い面に油通路を形成し、この油通路に当該油孔を連通連結することができる。 A flange for fixing the bearing device to the case is provided at the outer diameter portion of the outer ring, and the oil hole is inclined from the root of the outer ring to the counter bore on the side opposite to the pinion gear of the outer ring. It can be provided through.
With the pinion gear of the pinion shaft positioned inside the case, the body of the pinion shaft is rotatably supported by the through hole of the case via the bearing device, and the axial direction is provided at a plurality of circumferential positions of the through hole of the case. And an oil passage can be formed in the mating surface between the outer ring and the through hole of the case, and the oil hole can be connected to the oil passage.

当該ケースは、トランスファやデファレンシャルのケースとすることができる。 また、外輪には、シールを設けた位置よりもさらに軸受外方に張り出してなる円筒部を設ける一方、シールの外側に設けたダストシールの外周部分を外輪の当該円筒部に微小隙間を介して対向させることができる。   The case may be a transfer or differential case. The outer ring is provided with a cylindrical portion that protrudes further outward from the bearing than the position where the seal is provided, and the outer periphery of the dust seal provided on the outer side of the seal faces the cylindrical portion of the outer ring with a small gap. Can be made.

本発明は、構成簡素で良好な潤滑性を安定的に確保でき、転がり特性、寿命の向上に貢献できる。   The present invention has a simple structure and can stably ensure good lubricity, and can contribute to improvement of rolling characteristics and life.

本発明の最良の形態を図面に基づいて説明する。図１は、ピニオン軸支持用軸受装置を示す断面図、図２は、潤滑油の流れを示す図である。トランスファやデファレンシャルのケース１に、ピニオン軸２がピニオン軸支持用軸受装置３を介して回転自在に支持されている。   The best mode of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view showing a pinion shaft supporting bearing device, and FIG. 2 is a view showing a flow of lubricating oil. A pinion shaft 2 is rotatably supported by a transfer or differential case 1 via a pinion shaft support bearing device 3.

ピニオン軸２は、その胴部２ａの軸方向一端にピニオンギヤ２ｂが、また、軸方向他端にねじ軸部２ｃがそれぞれ設けられている。   The pinion shaft 2 is provided with a pinion gear 2b at one axial end of the body portion 2a and a screw shaft portion 2c at the other axial end.

このピニオン軸２は、そのピニオンギヤ２ｂがケース１の内部に位置する状態で胴部２ａがピニオン軸支持用軸受装置３を介してケース１の貫通孔１ａに回転自在に支持されている。ピニオン軸２の胴部２ａにカップリングスリーブ４をスプライン嵌合して、ピニオン軸２のねじ軸部２ｃにナット５を螺合装着することにより、ピニオン軸支持用軸受装置３に予圧が付与され、ピニオン軸２とピニオン軸支持用軸受装置３とが一体化される。   The pinion shaft 2 is rotatably supported by the through hole 1a of the case 1 via the pinion shaft support bearing device 3 with the pinion gear 2b positioned inside the case 1. A coupling sleeve 4 is spline-fitted to the body portion 2a of the pinion shaft 2 and a nut 5 is screwed and attached to the screw shaft portion 2c of the pinion shaft 2, whereby preload is applied to the pinion shaft support bearing device 3. The pinion shaft 2 and the pinion shaft support bearing device 3 are integrated.

なお、カップリングスリーブ４は、例えば自動車のプロペラシャフト（図示省略）に連結されるものであり、一般に、トランスファの場合には、ピニオン軸２の回転動力をプロペラシャフトへ出力する出力フランジと呼ばれる一方、デファレンシャルの場合には、前記プロペラシャフトの回転動力をピニオン軸２に入力するコンパニオンフランジと呼ばれる。   The coupling sleeve 4 is connected to, for example, a propeller shaft (not shown) of an automobile. Generally, in the case of a transfer, the coupling sleeve 4 is called an output flange that outputs the rotational power of the pinion shaft 2 to the propeller shaft. In the case of a differential, it is called a companion flange that inputs the rotational power of the propeller shaft to the pinion shaft 2.

ピニオン軸支持用軸受装置３は、単一の外輪６と、二つの内輪７，８と、複数の玉９と、二つの保持器１０，１１とを備えている。   The pinion shaft support bearing device 3 includes a single outer ring 6, two inner rings 7 and 8, a plurality of balls 9, and two cages 10 and 11.

外輪６は、軸方向二列の軌道面６ａ，６ｂを有するとともに軸方向両端にカウンタボア６ｃ，６ｄを有しており、さらに外径部分に径方向外向きに延びるフランジ６ｅが設けられている。   The outer ring 6 has two rows of raceway surfaces 6a and 6b in the axial direction, counter bores 6c and 6d at both ends in the axial direction, and a flange 6e extending radially outward at the outer diameter portion. .

この外輪６は、ケース１の貫通孔１ａに嵌合された状態で、そのフランジ６ｅがケース１にボルト１２で固定されている。一方の内輪７は、外輪６の一方の軌道面６ａに対向する単一の軌道面７ａを有するとともに軸方向内端にカウンタボア７ｂを有している。他方の内輪８は、外輪６の他方の軌道面６ｂと対向する単一の軌道面８ａを有するとともに軸方向内端にカウンタボア８ｂを有している。これら二つの内輪７，８は、ピニオン軸２の胴部２ａに外嵌される。外輪６の二列の軌道面６ａ，６ｂと二つの内輪７，８の各軌道面７ａ，８ａとの間に複数個の玉９が介装されており、各玉９列は保持器１０，１１で円周方向ほぼ等間隔に配置されている。   The outer ring 6 is fitted to the through hole 1 a of the case 1, and the flange 6 e is fixed to the case 1 with bolts 12. One inner ring 7 has a single raceway surface 7a facing one raceway surface 6a of the outer ring 6, and has a counter bore 7b at the inner end in the axial direction. The other inner ring 8 has a single raceway surface 8a facing the other raceway surface 6b of the outer ring 6, and a counter bore 8b at the inner end in the axial direction. These two inner rings 7, 8 are fitted on the body 2 a of the pinion shaft 2. A plurality of balls 9 are interposed between the two raceway surfaces 6a and 6b of the outer ring 6 and the raceway surfaces 7a and 8a of the two inner rings 7 and 8, respectively. 11 are arranged at substantially equal intervals in the circumferential direction.

ここで、ケース１内に収容される潤滑油でピニオン軸支持用軸受装置３を潤滑させるようにしているので、説明する。   Here, the pinion shaft supporting bearing device 3 is lubricated with the lubricating oil accommodated in the case 1 and will be described.

外輪６において、ピニオンギヤ２ｂと軸方向反対側（反ピニオンギヤ側）のカウンタボア６ｄにシール１３を装着して、ピニオンギヤ２ｂ側の端部をシールなしにして開放しているとともに、外径面のフランジ６ｅの根元側から反ピニオンギヤ側の軌道面６ｂよりも端縁側のカウンタボア６ｄへ貫通する油孔６ｆが設けられている。   In the outer ring 6, a seal 13 is attached to a counter bore 6d on the side opposite to the pinion gear 2b in the axial direction (on the opposite side of the pinion gear), the end on the pinion gear 2b side is opened without sealing, and a flange on the outer diameter surface is opened. An oil hole 6f penetrating from the base side of 6e to the counter bore 6d on the edge side of the raceway surface 6b on the side opposite to the pinion gear is provided.

ケース１の貫通孔１ａの円周方向複数箇所には、軸方向に沿う溝１ｂが設けられており、この溝１ｂによって外輪６とケース１の貫通孔１ａとの嵌め合い面に油通路が形成される。この溝１ｂからなる油通路に外輪６の油孔６ｆが連通連結されている。   Grooves 1b along the axial direction are provided at a plurality of positions in the circumferential direction of the through hole 1a of the case 1, and an oil passage is formed on the fitting surface between the outer ring 6 and the through hole 1a of the case 1 by the groove 1b. Is done. An oil hole 6f of the outer ring 6 is connected to the oil passage formed by the groove 1b.

シール１３は、胴体部としての金属環１４にゴムなどのリップ１５を加硫接着した構成である。金属環１４の外筒部分が外輪６のカウンタボア６ｄに圧入により嵌合されており、リップ１５が反ピニオンギヤ側の内輪８の肩部に所定の締め代をもって接触している。このリップ１５は、主として軸受内部の潤滑油漏洩を防止するように、軸受内側へ向けて開きうる形状になっている。このシール１３は、図示しないが、周知のタイプのものを用いることができる。   The seal 13 has a configuration in which a lip 15 such as rubber is vulcanized and bonded to a metal ring 14 as a body portion. The outer cylinder portion of the metal ring 14 is fitted into the counter bore 6d of the outer ring 6 by press fitting, and the lip 15 is in contact with the shoulder of the inner ring 8 on the side opposite to the pinion gear with a predetermined tightening margin. The lip 15 has a shape that can open toward the inside of the bearing so as to mainly prevent leakage of lubricating oil inside the bearing. Although this seal 13 is not shown, a well-known type can be used.

なお、シール１３のさらに外側には、ダストシール１６が設けられている。このダストシール１６は、上半分の断面がコの字形の金属環からなり、内周部分がカップリングスリーブ４の外周面に圧入により嵌合されており、外周部分が外輪６の張り出し円筒部６ｇに微小隙間６ｈを介して対向されている。   A dust seal 16 is provided on the outer side of the seal 13. The dust seal 16 is made of a metal ring having a U-shaped cross section in the upper half, and an inner peripheral portion is press-fitted to the outer peripheral surface of the coupling sleeve 4, and the outer peripheral portion is attached to the projecting cylindrical portion 6 g of the outer ring 6. It is opposed via a minute gap 6h.

このような構成であれば、図２に示すように、ケース１内の潤滑油が溝１ｂ、外輪６の油孔６ｆから、軸受内部空間における反ピニオンギヤ側の玉９列とシール１３との間に導入された後、矢印で示すように、ピニオンギヤ２ｂ側へ一方向に流れて、ケース１内に戻る。これにより、両方の玉９列にほぼ均等な量の潤滑油が供給されるので、長期にわたって偏りのない良好な潤滑が安定的に行われる。   With such a configuration, as shown in FIG. 2, the lubricating oil in the case 1 passes between the groove 1 b and the oil hole 6 f of the outer ring 6 between the ball 9 row on the side opposite to the pinion gear and the seal 13 in the bearing internal space. Then, as indicated by the arrow, it flows in one direction toward the pinion gear 2b and returns into the case 1. As a result, a substantially equal amount of lubricating oil is supplied to both the 9 rows of balls, so that good lubrication with no bias is stably performed over a long period of time.

以上説明したように、ピニオン軸支持用軸受装置３を複列外向きアンギュラ玉軸受としているから、従来例のような円すいころ軸受を用いる場合に比べてトルク低減が図れるとともに軸方向寸法をコンパクトにできる。しかも、ピニオン軸支持用軸受装置３の内部空間に潤滑油を一方向に流すようにしているから、各玉９列の潤滑性が安定して良好となり、長寿命化に貢献できる。   As described above, since the pinion shaft support bearing device 3 is a double-row outward angular contact ball bearing, torque can be reduced and the axial dimension can be made compact compared to the case of using a tapered roller bearing as in the conventional example. it can. In addition, since the lubricating oil is allowed to flow in one direction through the internal space of the pinion shaft supporting bearing device 3, the lubricity of each of the nine rows of balls becomes stable and can contribute to a longer life.

この他、上記実施形態のように、ピニオン軸２とピニオン軸支持用軸受装置３とをユニット化しているので、使用対象となるトランスファやデファレンシャルのケース１への組み込みの手間が軽減され、組立性が向上する。   In addition, since the pinion shaft 2 and the pinion shaft supporting bearing device 3 are unitized as in the above-described embodiment, the trouble of assembling the transfer and differential case 1 to be used into the case 1 is reduced. Will improve.

本発明の最良の形態に係るピニオン軸支持用軸受装置を示す断面図Sectional drawing which shows the pinion shaft support bearing apparatus which concerns on the best form of this invention 図１の潤滑油の流れを示す図The figure which shows the flow of the lubricating oil of FIG.

符号の説明Explanation of symbols

１ ケース
２ ピニオン軸
２ａ ピニオン軸の胴部
２ｂ ピニオンギヤ
３ ピニオン軸支持用軸受装置
６ 外輪
７，８ 内輪
１３ シール
１４ 金属環
１５ リップ 1 Case 2 Pinion shaft 2a Pinion shaft body 2b Pinion gear 3 Pinion shaft support bearing device 6 Outer ring 7, 8 Inner ring 13 Seal 14 Metal ring 15 Lip

Claims (3)

一端にピニオンギヤを有するピニオン軸を支持するピニオン軸支持用軸受装置において、
単一の外輪と二つの内輪との間に二列の玉を介装した複列外向きアンギュラ玉軸受とされ、その軸受内部空間の反ピニオンギヤ側がシールで閉塞されるとともにピニオンギヤ側が開放され、前記外輪に、外径側から反ピニオンギヤ側の玉列の軌道面よりも端縁側のカウンタボアへ貫通し反ピニオンギヤ側の玉列と前記シールとの間に潤滑油を導入する油孔が設けられている、ことを特徴とするピニオン軸用軸受装置。 In a pinion shaft support bearing device for supporting a pinion shaft having a pinion gear at one end,
A double-row outward angular ball bearing in which two rows of balls are interposed between a single outer ring and two inner rings, the anti-pinion gear side of the bearing inner space is closed with a seal and the pinion gear side is opened, The outer ring is provided with an oil hole that penetrates from the outer diameter side to the counter bore on the edge side than the raceway surface of the ball train on the anti-pinion gear side and introduces lubricating oil between the ball train on the anti-pinion gear side and the seal. A pinion shaft bearing device characterized by that. 前記外輪は、軸方向両端にカウンタボアを有し、前記二つの内輪は、それぞれ軸方向内端にカウンタボアを有し、前記シールは、前記外輪の反ピニオンギヤ側のカウンタボアに取り付けられる胴体部と、この胴体部の内周に設けられかつ前記反ピニオンギヤ側の内輪の肩部に接触するとともに、軸受内側へ向けて開きうるリップとを有している、ことを特徴とする請求項１に記載のピニオン軸用軸受装置。 The outer ring has counter bores at both ends in the axial direction, the two inner rings each have a counter bore at the inner end in the axial direction, and the seal is a body part attached to the counter bore on the side opposite to the pinion gear of the outer ring When contacts with the inner ring shoulder portion of the inner provided in the circumferential and the anti-pinion gear side of the body portion, and a lip which can open towards the bearing inside it in claim 1, wherein The pinion shaft bearing device described. 前記ピニオン軸を挿通した状態で支持するための貫通孔を有するケースと、A case having a through-hole for supporting the pinion shaft in a inserted state;
前記貫通孔に設けられ軸方向に沿った溝と、A groove provided in the through hole along the axial direction;
前記外輪の外径面に形成されたフランジと、A flange formed on the outer diameter surface of the outer ring;
を備え、With
前記外輪は、前記ケースの貫通孔に嵌合された状態で、前記フランジが前記ケースにボルト固定され、前記溝によって前記外輪と前記ケースの貫通孔との嵌め合い面に前記油孔に連通する油通路が形成される、ことを特徴とする請求項１または２に記載のピニオン軸支持用軸受装置。The flange is fixed to the case by bolts while the outer ring is fitted in the through hole of the case, and communicates with the oil hole on the fitting surface of the outer ring and the through hole of the case by the groove. The pinion shaft supporting bearing device according to claim 1, wherein an oil passage is formed.
JP2003409272A 2003-12-08 2003-12-08 Bearing device for pinion shaft support Expired - Fee Related JP4506160B2 (en)

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US7934871B2 (en) 2007-03-12 2011-05-03 Jtekt Corporation Double row ball bearing
JP5050582B2 (en) * 2007-03-12 2012-10-17 株式会社ジェイテクト Bearing device for rotating shaft support
JP5225208B2 (en) * 2009-06-09 2013-07-03 Ｇｋｎドライブラインジャパン株式会社 Power transmission device
JP2015021584A (en) * 2013-07-22 2015-02-02 日本車輌製造株式会社 Power device for electric carrier
CN104196987A (en) * 2014-08-08 2014-12-10 苏州苏净船用机械有限公司 Lubrication structure of propeller bearing
CN109681613B (en) * 2018-12-28 2024-01-05 宁夏天地奔牛实业集团有限公司 Mining speed reducer bearing end cover and mining speed reducer
JP2022173690A (en) * 2021-05-10 2022-11-22 株式会社小松製作所 Electric cylinder and work machine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182655A (en) * 1997-12-17 1999-07-06 Mitsubishi Motors Corp Lubrication structure of final reduction gear unit
JP2001004004A (en) * 1999-04-19 2001-01-09 Nissan Motor Co Ltd Toroidal type continuously variable transmission
JP2003232346A (en) * 2001-12-04 2003-08-22 Koyo Seiko Co Ltd Bearing device for supporting pinion shaft

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182655A (en) * 1997-12-17 1999-07-06 Mitsubishi Motors Corp Lubrication structure of final reduction gear unit
JP2001004004A (en) * 1999-04-19 2001-01-09 Nissan Motor Co Ltd Toroidal type continuously variable transmission
JP2003232346A (en) * 2001-12-04 2003-08-22 Koyo Seiko Co Ltd Bearing device for supporting pinion shaft

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