JP2003156128A - Pinion shaft supporting bearing device - Google Patents
Pinion shaft supporting bearing deviceInfo
- Publication number
- JP2003156128A JP2003156128A JP2001354552A JP2001354552A JP2003156128A JP 2003156128 A JP2003156128 A JP 2003156128A JP 2001354552 A JP2001354552 A JP 2001354552A JP 2001354552 A JP2001354552 A JP 2001354552A JP 2003156128 A JP2003156128 A JP 2003156128A
- Authority
- JP
- Japan
- Prior art keywords
- pinion shaft
- companion flange
- bearing
- rolling bearing
- pinion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- 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
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race ring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—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
-
- 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
- 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
- F16C19/16—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 a single row of balls
- F16C19/163—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 a single row of balls with angular contact
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
- F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Retarders (AREA)
- General Details Of Gearings (AREA)
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、自動車のディファ
レンシャル装置を構成するピニオン軸を、ディファレン
シャルケースの内側に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。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device for supporting a pinion shaft for rotatably supporting a pinion shaft, which constitutes a differential device of an automobile, inside a differential case.
【０００２】[0002]
【従来の技術】従来のディファレンシャル装置の構造を
図３に示す。2. Description of the Related Art The structure of a conventional differential device is shown in FIG.
【０００３】図３において、１はディファレンシャルケ
ースであり、このディファレンシャルケース１内に、左
右の車輪を差動連動する差動変速機構２、ピニオンギヤ
３、ピニオン軸４、ピニオン軸４を回転自在に支持する
転がり軸受５，６等が収納されている。In FIG. 3, reference numeral 1 denotes a differential case. In the differential case 1, a differential transmission mechanism 2 for differentially interlocking left and right wheels, a pinion gear 3, a pinion shaft 4, and a pinion shaft 4 are rotatably supported. Rolling bearings 5, 6 and the like are stored.
【０００４】ピニオンギヤ３は、差動変速機構２のリン
グギヤ２ａに噛合されており、ピニオン軸４の内端部に
一体形成されている。The pinion gear 3 meshes with the ring gear 2a of the differential transmission mechanism 2 and is integrally formed with the inner end portion of the pinion shaft 4.
【０００５】また、ピニオン軸４は、背面合わせに配置
した単列の円すいころ軸受からなる一対の転がり軸受
５，６にて、ディファレンシャルケース１の内側に回転
自在に支持されており、外端部にはプロペラシャフト
（図示せず）が連結されるコンパニオンフランジ７が設
けられている。The pinion shaft 4 is rotatably supported inside the differential case 1 by a pair of rolling bearings 5 and 6 composed of single-row tapered roller bearings arranged back to back, and its outer end portion is rotatably supported. Is provided with a companion flange 7 to which a propeller shaft (not shown) is connected.
【０００６】また、転がり軸受５，６は、各々ディファ
レンシャルケース１の鍛造製の軸受ケース部１ａに形成
した軸受装着用の環状壁１３，１４の内周面に装着され
ている。なお、コンパニオンフランジ側の転がり軸受５
は軸受ケース部１ａの小径側開口部から組み込まれ、ピ
ニオンギヤ側の転がり軸受６は軸受ケース部１ａの大径
側開口部から組み込まれ、両転がり軸受５，６間には位
置決め用のスペーサ８が介装されている。転がり軸受
５，６は、ピニオン軸４の外端部にナット１５を螺合
し、コンパニオンフランジ７に締結することで、ピニオ
ンギヤ３とコンパニオンフランジ７の間で十分な予圧を
付与して固定される。The rolling bearings 5 and 6 are mounted on the inner peripheral surfaces of bearing mounting annular walls 13 and 14 formed on the forged bearing case portion 1a of the differential case 1, respectively. The rolling bearing 5 on the companion flange side
Is incorporated from the small diameter side opening of the bearing case portion 1a, the rolling bearing 6 on the pinion gear side is incorporated from the large diameter side opening portion of the bearing case portion 1a, and a positioning spacer 8 is provided between both rolling bearings 5 and 6. It is installed. The rolling bearings 5 and 6 are fixed by applying a sufficient preload between the pinion gear 3 and the companion flange 7 by screwing a nut 15 onto the outer end portion of the pinion shaft 4 and fastening the nut 15 to the companion flange 7. .
【０００７】さらに、ディファレンシャルケース１内に
は、潤滑用のオイルが運転停止状態においてレベルＬに
て貯留されている。オイルは、運転時にリングギヤ２ａ
の回転に伴って跳ね上げられ、軸受ケース部１ａ内の環
状壁１３，１４間に形成したオイル導入路１１を通って
転がり軸受５，６に導かれ、さらにオイル還流路（図示
せず）を通って戻される。なお、ピニオン軸４の外端部
側の外周面と軸受ケース部１ａの内周面との間には、オ
イルの漏洩防止のためのオイルシール９が装着されてお
り、かつ、オイルシール９を隠蔽するシール保護カップ
１０が取付けられている。Further, lubricating oil is stored at a level L in the differential case 1 when the operation is stopped. The oil is the ring gear 2a during operation.
Of the bearing case portion 1a is guided up to the rolling bearings 5 and 6 through the oil introduction passage 11 formed between the annular walls 13 and 14 in the bearing case portion 1a, and further to an oil return passage (not shown). Returned through. An oil seal 9 for preventing oil leakage is mounted between the outer peripheral surface of the pinion shaft 4 on the outer end side and the inner peripheral surface of the bearing case portion 1a, and the oil seal 9 is provided. A concealing seal protection cup 10 is attached.
【０００８】[0008]
【発明が解決しようとする課題】従来のディファレンシ
ャル装置の場合、コンパニオンフランジ側の転がり軸受
５とコンパニオンフランジ７が、互いの端面を突き合せ
て並設されているため、軸心方向に長くなり、ディファ
レンシャル装置が大型化するという問題があった。In the case of the conventional differential device, the rolling bearing 5 and the companion flange 7 on the companion flange side are arranged side by side with their end faces abutting, so that they become long in the axial direction, There is a problem that the differential device becomes large.
【０００９】この発明は、軸心方向の長さを短くしてデ
ィファレンシャル装置の小型化が図れるピニオン軸支持
用軸受装置を提供することを目的とする。It is an object of the present invention to provide a bearing device for supporting a pinion shaft, which can shorten the length in the axial direction to downsize the differential device.
【００１０】[0010]
【課題を解決するための手段】本発明は、ピニオン軸の
一端に設けたピニオンギヤと、他端に外嵌したコンパニ
オンフランジとの間に、前記ピニオン軸をケースに対し
て回転自在に支持する軸心方向に並設した一対の転がり
軸受を装着してなるピニオン軸支持用軸受装置であっ
て、前記コンパニオンフランジは、コンパニオンフラン
ジ側の転がり軸受の内輪と前記ピニオン軸との間に介装
される円筒状の介装部を有し、かつ、外周面にコンパニ
オンフランジ側の転がり軸受の内輪の端面をピニオンギ
ヤ方向に押圧する押圧部を形成してなり、前記コンパニ
オンフランジを締結手段にてピニオンギヤ方向に締結す
ることにより、前記押圧部を介して前記転がり軸受に予
圧を付与して前記ピニオン軸に固定することを特徴とす
るものである。SUMMARY OF THE INVENTION According to the present invention, a shaft for rotatably supporting a pinion shaft with respect to a case between a pinion gear provided at one end of the pinion shaft and a companion flange externally fitted at the other end. A bearing device for supporting a pinion shaft, comprising a pair of rolling bearings arranged in parallel in the axial direction, wherein the companion flange is interposed between the inner ring of the rolling bearing on the companion flange side and the pinion shaft. It has a cylindrical interposition part, and is formed with a pressing part on the outer peripheral surface for pressing the end face of the inner ring of the rolling bearing on the companion flange side in the pinion gear direction, and the companion flange in the pinion gear direction by the fastening means. By fastening, the rolling bearing is preloaded through the pressing portion and fixed to the pinion shaft.
【００１１】本発明のピニオン軸支持用軸受装置による
と、コンパニオンフランジは、介装部をコンパニオンフ
ランジ側の転がり軸受の内輪とピニオン軸との間に介装
して設けられており、コンパニオンフランジを転がり軸
受に重ねて装着する分、軸心方向の長さを短くでき、デ
ィファレンシャル装置の小型化が図れる。According to the bearing device for supporting the pinion shaft of the present invention, the companion flange is provided with the interposition portion interposed between the inner ring of the rolling bearing on the companion flange side and the pinion shaft, and the companion flange is provided. The length in the axial direction can be shortened by mounting the rolling bearing on top of each other, and the differential device can be miniaturized.
【００１２】また、転がり軸受とピニオン軸との間にコ
ンパニオンフランジを介装することで、転がり軸受が径
方向外側に配置され、転がり軸受の軌道径が大きくな
り、その結果、転動体の個数を増やすことができ、負荷
容量が大きくなる。Further, by inserting the companion flange between the rolling bearing and the pinion shaft, the rolling bearing is arranged on the outer side in the radial direction, and the raceway diameter of the rolling bearing is increased. As a result, the number of rolling elements is reduced. It is possible to increase the load capacity.
【００１３】なお、コンパニオンフランジ側の転がり軸
受の種類は特に限定されるものではないが、例えば、ア
ンギュラ玉軸受とする。The type of rolling bearing on the companion flange side is not particularly limited, but for example, an angular ball bearing is used.
【００１４】このように、コンパニオンフランジ側の転
がり軸受をアンギュラ玉軸受とすることで、転がり軸受
の摩擦抵抗が小さくなり、回転トルクを小さくできる。
しかも、転がり軸受とピニオン軸との間にコンパニオン
フランジを介装することで、回転トルクを小さくしなが
らも十分な負荷容量が得られ、ディファレンシャル装置
の効率が向上する。As described above, the rolling bearing on the companion flange side is an angular contact ball bearing, so that the frictional resistance of the rolling bearing is reduced and the rotational torque can be reduced.
Moreover, by providing the companion flange between the rolling bearing and the pinion shaft, sufficient load capacity can be obtained while reducing the rotational torque, and the efficiency of the differential device is improved.
【００１５】[0015]
【発明の実施の形態】（実施の形態１）本発明の実施の
形態１について、図１を用いて説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS (Embodiment 1) Embodiment 1 of the present invention will be described with reference to FIG.
【００１６】図１は、実施の形態１におけるピニオン軸
支持用軸受装置を適用したディファレンシャル装置の断
面図を示している。FIG. 1 is a sectional view of a differential device to which the bearing device for supporting a pinion shaft according to the first embodiment is applied.
【００１７】この実施の形態１のピニオン軸支持用軸受
装置は、コンパニオンフランジ側の転がり軸受５が単列
のアンギュラ玉軸受にて構成されており、かつ、コンパ
ニオンフランジ７が当該転がり軸受５とピニオン軸４の
間に介装されていることを特徴とするものである。In the bearing device for supporting the pinion shaft according to the first embodiment, the rolling bearing 5 on the companion flange side is composed of a single row of angular ball bearings, and the companion flange 7 is connected to the rolling bearing 5 and the pinion. It is characterized in that it is interposed between the shafts 4.
【００１８】なお、その他の構成は図３の例と同一であ
り、同一部分には同一符号を付してその説明を省略す
る。The rest of the configuration is the same as that of the example of FIG. 3, and the same parts are denoted by the same reference numerals and the description thereof is omitted.
【００１９】転がり軸受５は、内輪５１，外輪５２，保
持器５４にて保持された玉群５３からなる。The rolling bearing 5 comprises an inner ring 51, an outer ring 52, and a ball group 53 held by a cage 54.
【００２０】コンパニオンフランジ７のピニオン軸４に
外嵌される円筒部の先端部分は、転がり軸受５の内輪５
１とピニオン軸４の間に介装される介装部７２となり、
外周面には転がり軸受５の内輪５１の端面をピニオンギ
ヤ方向に押圧する環状突起の押圧部７３が一体形成され
ている。The tip of the cylindrical portion of the companion flange 7 which is externally fitted to the pinion shaft 4 has an inner ring 5 of the rolling bearing 5.
1 and the pinion shaft 4 are interposed parts 72,
The outer peripheral surface is integrally formed with a pressing portion 73 of an annular protrusion that presses the end surface of the inner ring 51 of the rolling bearing 5 in the pinion gear direction.
【００２１】そして、転がり軸受５をコンパニオンフラ
ンジ７の介装部７２の外周面に圧入すると共に、コンパ
ニオンフランジ７をピニオン軸４のドライブシャフト側
の小径部４３にスプライン嵌合する。さらに、ピニオン
軸４のドライブシャフト側端部に締結手段となるナット
１５を螺合し、コンパニオンフランジ７に締結する。Then, the rolling bearing 5 is press-fitted into the outer peripheral surface of the interposed portion 72 of the companion flange 7, and the companion flange 7 is spline fitted to the small diameter portion 43 of the pinion shaft 4 on the drive shaft side. Further, a nut 15 serving as a fastening means is screwed onto the end portion of the pinion shaft 4 on the drive shaft side and fastened to the companion flange 7.
【００２２】これにより、コンパニオンフランジ７の介
装部７２の先端と、ピニオン軸４の小径部４３の最奥部
分の段部４１との間に隙間が形成された状態で、コンパ
ニオンフランジ７の押圧部７３が転がり軸受５の内輪５
１の端面に当接し、内輪５１をピニオンギヤ方向に押圧
する。その結果、スペーサ８を介して並設された転がり
軸受５，６が、ピニオンギヤ３とコンパニオンフランジ
７にて挟み込まれ、予圧を付与されてピニオン軸４に固
定される。As a result, the companion flange 7 is pressed while a gap is formed between the tip of the interposed portion 72 of the companion flange 7 and the deepest step 41 of the small diameter portion 43 of the pinion shaft 4. The portion 73 is the inner ring 5 of the rolling bearing 5.
The inner ring 51 is pressed against the end face of No. 1 in the pinion gear direction. As a result, the rolling bearings 5 and 6 arranged side by side via the spacer 8 are sandwiched by the pinion gear 3 and the companion flange 7, and are preloaded and fixed to the pinion shaft 4.
【００２３】このように構成されたピニオン軸支持用軸
受装置によると、コンパニオンフランジ７は、介装部７
２をコンパニオンフランジ側の転がり軸受５の内輪５１
とピニオン軸４との間に介装して設けられており、コン
パニオンフランジ７を転がり軸受５に重ねて装着する
分、軸心方向の長さを短くでき、ディファレンシャル装
置の小型化が図れる。According to the bearing device for supporting the pinion shaft constructed as described above, the companion flange 7 has the interposition part 7
2 the inner ring 51 of the rolling bearing 5 on the companion flange side
And the pinion shaft 4, the companion flange 7 is mounted on the rolling bearing 5 in an overlapping manner, so that the axial length can be shortened and the differential device can be downsized.
【００２４】また、転がり軸受５をアンギュラ玉軸受と
することで、転がり軸受５の摩擦抵抗が小さくなり、回
転トルクを小さくできる。しかも、転がり軸受５とピニ
オン軸４の間にコンパニオンフランジ７の介装部７２を
介装することで、転がり軸受が径方向外側に配置され、
転がり軸受５の軌道径が大きくなり、その結果、玉５３
の個数を増やすことができ、負荷容量が大きくなる。こ
のように、回転トルクを小さくしながらも十分な負荷容
量が得られ、ディファレンシャル装置の効率が向上す
る。Further, by making the rolling bearing 5 an angular ball bearing, the frictional resistance of the rolling bearing 5 becomes small, and the rotational torque can be made small. Moreover, by interposing the interposition portion 72 of the companion flange 7 between the rolling bearing 5 and the pinion shaft 4, the rolling bearing is arranged radially outward,
The raceway diameter of the rolling bearing 5 increases, and as a result, the balls 53
The number of cells can be increased, and the load capacity can be increased. In this way, a sufficient load capacity can be obtained while reducing the rotational torque, and the efficiency of the differential device is improved.
【００２５】また、コンパニオンフランジ７の外周面に
環状突起の押圧部７３を形成したことで、転がり軸受５
の内輪５１の端面を広範囲に渡って押圧でき、転がり軸
受５，６に確実に予圧を付与することができる。Further, since the pressing portion 73 of the annular projection is formed on the outer peripheral surface of the companion flange 7, the rolling bearing 5
The end surface of the inner ring 51 can be pressed over a wide range, and the preload can be reliably applied to the rolling bearings 5 and 6.
【００２６】さらに、コンパニオンフランジ７の内周面
には、介装部７２にまで渡ってスプライン７１が形成さ
れており、軸心方向の長さを短くしても、回転トルクの
伝達に必要なスプライン７１の長さを十分に確保でき
る。Further, a spline 71 is formed on the inner peripheral surface of the companion flange 7 up to the interposition part 72, which is necessary for transmitting the rotational torque even if the axial length is shortened. A sufficient length of the spline 71 can be secured.
【００２７】なお、締結手段はナット１５に限らず、ピ
ニオン軸４のドライブシャフト側端部をかしめてなるも
のであってもよい。The fastening means is not limited to the nut 15 and may be one in which the end of the pinion shaft 4 on the drive shaft side is swaged.
【００２８】また、コンパニオンフランジ７の押圧部７
３は環状突起でなく、転がり軸受５の内輪５１の端面に
当接する段部からなるものであってもよい。The pressing portion 7 of the companion flange 7
3 is not an annular projection, but may be a stepped portion that comes into contact with the end surface of the inner ring 51 of the rolling bearing 5.
【００２９】また、転がり軸受５の種類は特に限定され
るものではなく、例えば、図３に示したような円すいこ
ろ軸受にて構成されていてもよい。Further, the type of the rolling bearing 5 is not particularly limited, and may be constituted by a tapered roller bearing as shown in FIG. 3, for example.
【００３０】さらに、ピニオンギヤ側の転がり軸受６の
種類も特に限定されるものではなく、例えば、タンデム
型の複列のアンギュラ玉軸受や円筒ころ軸受にて構成さ
れていてもよい。これにより、円すいころ軸受に比べて
トルクの低減が図れる。Further, the type of the rolling bearing 6 on the pinion gear side is not particularly limited, and may be constituted by, for example, a tandem type double row angular contact ball bearing or a cylindrical roller bearing. As a result, the torque can be reduced as compared with the tapered roller bearing.
【００３１】（実施の形態２）本発明の実施の形態２に
ついて、図２を用いて説明する。(Second Embodiment) A second embodiment of the present invention will be described with reference to FIG.
【００３２】図２は、実施の形態２におけるディファレ
ンシャル装置のピニオン軸支持用軸受装置の部分断面図
を示している。FIG. 2 is a partial sectional view of a bearing device for supporting a pinion shaft of a differential device according to the second embodiment.
【００３３】図２において、１はディファレンシャルケ
ース、３は差動変速機構のリングギヤ（図示せず）に噛
合したピニオンギヤ、４はピニオンギヤ３に一体形成し
たピニオン軸、２０はピニオン軸４をディファレンシャ
ルケース１に対して回転自在に支持する軸受ユニットで
ある。In FIG. 2, 1 is a differential case, 3 is a pinion gear meshing with a ring gear (not shown) of a differential transmission mechanism, 4 is a pinion shaft integrally formed with the pinion gear 3, and 20 is a differential case 1 with a pinion shaft 4. The bearing unit rotatably supports the bearing unit.
【００３４】軸受ユニット２０は、コンパニオンフラン
ジ側の単列のアンギュラ玉軸受からなる転がり軸受５
と、ピニオンギヤ側のタンデム型の複列のアンギュラ玉
軸受からなる転がり軸受６にて構成されている。すなわ
ち、転がり軸受５は、内輪２１，外輪２６，保持器３４
にて保持された玉群３１からなり、転がり軸受６は、内
輪２２，外輪２６，保持器３５，３６にて保持された玉
群３２，３３からなり、両内輪２１，２２どうしを軸心
方向に突合せると共に、グリースを充填して軸心方向両
端をシール部材３７，３８にて密封し、かつ外輪２６を
単一としたユニットものにて形成されている。The bearing unit 20 is a rolling bearing 5 composed of a single row of angular ball bearings on the companion flange side.
And a rolling bearing 6 composed of a tandem type double-row angular contact ball bearing on the pinion gear side. That is, the rolling bearing 5 includes the inner ring 21, the outer ring 26, and the cage 34.
The rolling bearing 6 includes the inner ring 22, the outer ring 26, and the ball groups 32 and 33 held by the cages 35 and 36, and the inner rings 21 and 22 are axially aligned with each other. The outer ring 26 is united with the outer ring 26 in a single unit.
【００３５】軸受ユニット２０は、製造段階で、内輪２
１，２２、外輪２６、保持器３４，３５，３６にて保持
した玉群３１，３２，３３を組み付けることで正確な予
圧調整を行っておく。The bearing unit 20 is manufactured at the manufacturing stage.
Accurate preload adjustment is performed by assembling the ball groups 31, 32, 33 held by the outer races 1, 22, the outer ring 26, and the cages 34, 35, 36.
【００３６】また、コンパニオンフランジ７のピニオン
軸４に外嵌される円筒部の先端部分は、転がり軸受５の
内輪２１とピニオン軸４の間に介装される介装部７２と
なり、外周面には転がり軸受５の内輪２１の端面をピニ
オンギヤ方向に押圧する段部からなる押圧部７３が形成
されている。The tip portion of the cylindrical portion of the companion flange 7 which is externally fitted on the pinion shaft 4 serves as an interposing portion 72 interposed between the inner ring 21 of the rolling bearing 5 and the pinion shaft 4 and is provided on the outer peripheral surface. The rolling bearing 5 has a pressing portion 73 formed of a step portion that presses the end surface of the inner ring 21 in the pinion gear direction.
【００３７】そして、軸受ユニット２０の転がり軸受５
の内輪２１をコンパニオンフランジ７の介装部７２の外
周面に圧入すると共に、転がり軸受６の内輪２２をピニ
オン軸４にドライブシャフト側から圧入し、かつ、コン
パニオンフランジ７をピニオン軸４のドライブシャフト
側の小径部４３にスプライン嵌合する。さらに、ピニオ
ン軸４のドライブシャフト側端部を径方向外向きにかし
め、当該締結手段となるかしめ４２によって、コンパニ
オンフランジ７をピニオンギヤ方向に締め付ける。The rolling bearing 5 of the bearing unit 20
Of the inner ring 22 of the rolling bearing 6 is press-fitted into the pinion shaft 4 from the drive shaft side, and the companion flange 7 of the pinion shaft 4 The small diameter portion 43 on the side is spline-fitted. Further, the end of the pinion shaft 4 on the drive shaft side is crimped outward in the radial direction, and the companion flange 7 is clamped in the pinion gear direction by the caulking 42 serving as the fastening means.
【００３８】これにより、コンパニオンフランジ７の介
装部７２の先端と、ピニオン軸４の小径部４３の最奥部
分の段部４１との間に隙間が形成された状態で、コンパ
ニオンフランジ７の押圧部７３が転がり軸受５の内輪２
１の端面に当接し、内輪２１をピニオンギヤ方向に押圧
する。その結果、軸受ユニット２０が、ピニオンギヤ３
とコンパニオンフランジ７にて挟み込まれ、予圧を付与
されてピニオン軸４に固定される。As a result, the companion flange 7 is pressed in a state in which a gap is formed between the tip of the interposed portion 72 of the companion flange 7 and the deepest step 41 of the small diameter portion 43 of the pinion shaft 4. The portion 73 is the inner ring 2 of the rolling bearing 5.
The inner ring 21 is pressed in the pinion gear direction. As a result, the bearing unit 20 moves to the pinion gear 3
It is sandwiched by the companion flange 7, is preloaded, and is fixed to the pinion shaft 4.
【００３９】さらに、ディファレンシャルケース１の外
面に、外輪２６に設けたフランジ３０をボルト４０にて
固定する。Further, the flange 30 provided on the outer ring 26 is fixed to the outer surface of the differential case 1 with bolts 40.
【００４０】このように構成されたピニオン軸支持用軸
受装置によると、コンパニオンフランジ７は、介装部７
２をコンパニオンフランジ側の転がり軸受５の内輪２１
とピニオン軸４との間に介装して設けられており、コン
パニオンフランジ７を転がり軸受５に重ねて装着する
分、軸心方向の長さが短くなり、ディファレンシャル装
置の小型化が図れる。According to the bearing device for supporting the pinion shaft thus configured, the companion flange 7 is provided with the interposition part 7
2 the inner ring 21 of the rolling bearing 5 on the companion flange side
And the pinion shaft 4, the companion flange 7 is mounted on the rolling bearing 5 in an overlapping manner, so that the axial length is shortened and the differential device can be downsized.
【００４１】また、転がり軸受５をアンギュラ玉軸受と
することで、転がり軸受５の摩擦抵抗が小さくなり、回
転トルクを小さくできる。しかも、転がり軸受５とピニ
オン軸４の間にコンパニオンフランジ７の介装部７２を
介装することで、転がり軸受が径方向外側に配置され、
転がり軸受５の軌道径が大きくなり、その結果、玉３１
の個数を増やすことができ、負荷容量が大きくなる。こ
のように、回転トルクを小さくしながらも十分な負荷容
量が得られ、ディファレンシャル装置の効率が向上す
る。By using the rolling bearing 5 as an angular ball bearing, the frictional resistance of the rolling bearing 5 can be reduced and the rotational torque can be reduced. Moreover, by interposing the interposition portion 72 of the companion flange 7 between the rolling bearing 5 and the pinion shaft 4, the rolling bearing is arranged radially outward,
The raceway diameter of the rolling bearing 5 increases, and as a result, the balls 31
The number of cells can be increased, and the load capacity can be increased. In this way, a sufficient load capacity can be obtained while reducing the rotational torque, and the efficiency of the differential device is improved.
【００４２】また、コンパニオンフランジ７の内周面に
は、介装部７２にまで渡ってスプライン７１が形成され
ており、軸心方向の長さが小さくても、回転トルクの伝
達に必要なスプライン７１の長さを十分に確保できる。Further, a spline 71 is formed on the inner peripheral surface of the companion flange 7 to extend to the interposition part 72, and even if the length in the axial direction is small, the spline required to transmit the rotational torque. A sufficient length of 71 can be secured.
【００４３】さらに、軸受ユニット２０が軸心方向両端
をシール部材３７，３８にて密封してなるグリース潤滑
であり、オイル潤滑のように、ディファレンシャルケー
ス１内にオイル導入路やオイル還流路を形成する必要が
なく、ディファレンシャル装置の小型，軽量化が図れ
る。しかも、軸受ユニット２０はディファレンシャル装
置のオイル中の異物の影響を受けないため、軸受寿命が
向上する。Further, the bearing unit 20 is grease lubricated by sealing both ends in the axial direction with the seal members 37 and 38, and like the oil lubrication, the oil introduction passage and the oil return passage are formed in the differential case 1. The differential device can be made smaller and lighter. Moreover, since the bearing unit 20 is not affected by foreign matter in the oil of the differential device, the bearing life is improved.
【００４４】なお、締結手段はかしめ４２に限らず、ナ
ットによるものであってもよい。The fastening means is not limited to the caulking 42, but may be a nut.
【００４５】また、転がり軸受５の種類は特に限定され
るものではなく、例えば、円すいころ軸受やタンデム型
の複列のアンギュラ玉軸受にて構成されていてもよい。The type of the rolling bearing 5 is not particularly limited, and may be, for example, a tapered roller bearing or a tandem type double row angular contact ball bearing.
【００４６】さらに、ピニオンギヤ側の転がり軸受６の
種類も特に限定されるものではなく、例えば、円すいこ
ろ軸受や円筒ころ軸受にて構成されていてもよい。Further, the type of the rolling bearing 6 on the side of the pinion gear is not particularly limited, and may be, for example, a tapered roller bearing or a cylindrical roller bearing.
【００４７】[0047]
【発明の効果】本発明のピニオン軸支持用軸受装置によ
れば、コンパニオンフランジの介装部を転がり軸受の内
輪とピニオン軸との間に介装することで、軸心方向の長
さを短くしてディファレンシャル装置の小型化が図れ
る。According to the bearing device for supporting a pinion shaft of the present invention, the length of the companion flange is shortened in the axial direction by interposing the interposition part of the companion flange between the inner ring of the rolling bearing and the pinion shaft. Therefore, the differential device can be downsized.
【００４８】また、転がり軸受とピニオン軸との間にコ
ンパニオンフランジを介装することで、負荷容量が大き
くなるという効果が得られる。Further, by providing the companion flange between the rolling bearing and the pinion shaft, the effect of increasing the load capacity can be obtained.
【図１】本発明の実施の形態１におけるピニオン軸支持
用軸受装置を適用したディファレンシャル装置の断面図
である。FIG. 1 is a sectional view of a differential device to which a pinion shaft supporting bearing device according to a first embodiment of the present invention is applied.
【図２】本発明の実施の形態２におけるディファレンシ
ャル装置のピニオン軸支持用軸受装置の部分断面図であ
る。FIG. 2 is a partial sectional view of a bearing device for supporting a pinion shaft of a differential device according to a second embodiment of the present invention.
【図３】従来例におけるディファレンシャル装置の断面
図である。FIG. 3 is a cross-sectional view of a conventional differential device.
１ ディファレンシャルケース ２ 差動変速機構 ２ａ リングギヤ ３ ピニオンギヤ ４ ピニオン軸 ５ コンパニオンフランジ側の転がり軸受 ６ ピニオンギヤ側の転がり軸受 ７ コンパニオンフランジ ２０ 軸受ユニット １５ ナット（締結手段） ４２ かしめ（締結手段） ７２ 介装部 ７３ 押圧部 1 differential case 2 differential transmission 2a ring gear 3 pinion gear 4 pinion shaft 5 Rolling bearing on companion flange side 6 Pinion gear side rolling bearing 7 companion flange 20 bearing unit 15 Nut (fastening means) 42 Caulking (fastening means) 72 Interposer 73 Pressing part
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ１６Ｃ 25/06 Ｆ１６Ｃ 25/06 35/073 35/073 Ｆ１６Ｈ 48/00 Ｆ１６Ｈ 1/38 (72)発明者 耕田 寛一 大阪市中央区南船場三丁目５番８号 光洋 精工株式会社内 Ｆターム(参考） 3J012 AB04 BB03 BB05 CB01 CB06 FB10 FB12 GB10 3J017 AA02 AA10 BA10 CA06 DA01 DB02 3J027 FA36 FA37 FB02 GA02 HC14 3J063 AA02 AB04 AB13 AC11 BA04 BB41 CA05 CB52 CB57 CD03 CD42 3J101 AA02 AA16 AA25 AA32 AA42 AA44 AA54 AA62 AA82 AA83 BA64 BA77 FA53 GA01 ─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. 7 Identification code FI theme code (reference) F16C 25/06 F16C 25/06 35/073 35/073 F16H 48/00 F16H 1/38 (72) Inventor Kan'ichi KODA 3-5-8 Minamisenba, Chuo-ku, Osaka F-term at Koyo Seiko Co., Ltd. (reference) 3J012 AB04 BB03 BB05 CB01 CB06 FB10 FB12 GB10 3J017 AA02 AA10 BA10 CA06 DA01 DB02 3J027 FA36 FA37 FB02 GA02 HC14 30406 A02 AC11 BA04 BB41 CA05 CB52 CB57 CD03 CD42 3J101 AA02 AA16 AA25 AA32 AA42 AA44 AA54 AA62 AA82 AA83 BA64 BA77 FA53 GA01
Claims (2)
と、他端に外嵌したコンパニオンフランジとの間に、前
記ピニオン軸をケースに対して回転自在に支持する軸心
方向に並設した一対の転がり軸受を装着してなるピニオ
ン軸支持用軸受装置であって、 前記コンパニオンフランジは、コンパニオンフランジ側
の転がり軸受の内輪と前記ピニオン軸との間に介装され
る円筒状の介装部を有し、かつ、外周面にコンパニオン
フランジ側の転がり軸受の内輪の端面をピニオンギヤ方
向に押圧する押圧部を形成してなり、 前記コンパニオンフランジを締結手段にてピニオンギヤ
方向に締結することにより、前記押圧部を介して前記転
がり軸受に予圧を付与して前記ピニオン軸に固定するこ
とを特徴とするピニオン軸支持用軸受装置。1. A pair of pinion gears provided at one end of a pinion shaft and a companion flange fitted to the other end of the pinion shaft, the pair of pinion shafts being arranged side by side in the axial direction to rotatably support the pinion shaft with respect to a case. A bearing device for supporting a pinion shaft mounted with a rolling bearing, wherein the companion flange has a cylindrical interposition part interposed between an inner ring of the rolling bearing on the companion flange side and the pinion shaft. And, the outer peripheral surface is formed with a pressing portion that presses the end surface of the inner ring of the rolling bearing on the companion flange side in the pinion gear direction, and by pressing the companion flange in the pinion gear direction with a fastening means, the pressing portion A bearing device for supporting a pinion shaft, which is fixed to the pinion shaft by applying a preload to the rolling bearing through the pinion shaft.
アンギュラ玉軸受としたことを特徴とする請求項１記載
のピニオン軸支持用軸受装置。2. The bearing device for supporting a pinion shaft according to claim 1, wherein the rolling bearing on the companion flange side is an angular ball bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001354552A JP2003156128A (en) | 2001-11-20 | 2001-11-20 | Pinion shaft supporting bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001354552A JP2003156128A (en) | 2001-11-20 | 2001-11-20 | Pinion shaft supporting bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003156128A true JP2003156128A (en) | 2003-05-30 |
Family
ID=19166397
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001354552A Pending JP2003156128A (en) | 2001-11-20 | 2001-11-20 | Pinion shaft supporting bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003156128A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005090596A (en) * | 2003-09-16 | 2005-04-07 | Nissan Motor Co Ltd | Drive pinion supporting structure for final reduction gear |
| JP2005344781A (en) * | 2004-06-01 | 2005-12-15 | Nissan Diesel Motor Co Ltd | Sealing device of driving system |
| EP1586794A3 (en) * | 2004-04-13 | 2006-08-23 | Dana Corporation | Differential with pinion bearings supported on input yoke |
| EP1719926A1 (en) * | 2004-02-23 | 2006-11-08 | JTEKT Corporation | Skew contact double ball bearing and pre-load adding method therefor |
| EP1734268A1 (en) * | 2004-02-20 | 2006-12-20 | Jtekt Corporation | Oblique contact ball bearing and bearing device for supporting pinion shaft |
| JP2011089557A (en) * | 2009-10-21 | 2011-05-06 | Gkn Driveline Japan Ltd | Power transmission device |
| WO2013094802A1 (en) * | 2011-12-23 | 2013-06-27 | 한국생산기술연구원 | Direct drive-type drive module for differential gear in electric vehicle |
| KR20190000152A (en) * | 2017-06-22 | 2019-01-02 | 주식회사 베어링아트 | Double row bearing for pinion shaft and differential device comprising the same |
| CN113551019A (en) * | 2020-04-08 | 2021-10-26 | 沃尔沃汽车公司 | Differential assembly |
-
2001
- 2001-11-20 JP JP2001354552A patent/JP2003156128A/en active Pending
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005090596A (en) * | 2003-09-16 | 2005-04-07 | Nissan Motor Co Ltd | Drive pinion supporting structure for final reduction gear |
| JP4501384B2 (en) * | 2003-09-16 | 2010-07-14 | 日産自動車株式会社 | Drive pinion support structure of final reduction gear |
| EP1734268A1 (en) * | 2004-02-20 | 2006-12-20 | Jtekt Corporation | Oblique contact ball bearing and bearing device for supporting pinion shaft |
| EP1734268A4 (en) * | 2004-02-20 | 2007-04-25 | Jtekt Corp | Oblique contact ball bearing and bearing device for supporting pinion shaft |
| EP1719926A1 (en) * | 2004-02-23 | 2006-11-08 | JTEKT Corporation | Skew contact double ball bearing and pre-load adding method therefor |
| EP1719926A4 (en) * | 2004-02-23 | 2007-04-25 | Jtekt Corp | Skew contact double ball bearing and pre-load adding method therefor |
| US7594759B2 (en) | 2004-02-23 | 2009-09-29 | Jtekt Corporation | Oblique contact double row ball bearing and method of imparting preload in the ball bearing |
| EP1586794A3 (en) * | 2004-04-13 | 2006-08-23 | Dana Corporation | Differential with pinion bearings supported on input yoke |
| JP4676717B2 (en) * | 2004-06-01 | 2011-04-27 | Ｕｄトラックス株式会社 | Drivetrain sealing device |
| JP2005344781A (en) * | 2004-06-01 | 2005-12-15 | Nissan Diesel Motor Co Ltd | Sealing device of driving system |
| JP2011089557A (en) * | 2009-10-21 | 2011-05-06 | Gkn Driveline Japan Ltd | Power transmission device |
| WO2013094802A1 (en) * | 2011-12-23 | 2013-06-27 | 한국생산기술연구원 | Direct drive-type drive module for differential gear in electric vehicle |
| JP2014503776A (en) * | 2011-12-23 | 2014-02-13 | コリア インスティチュート オブ インダストリアル テクノロジー | Direct-drive drive module for differential gears for electric vehicles |
| KR20190000152A (en) * | 2017-06-22 | 2019-01-02 | 주식회사 베어링아트 | Double row bearing for pinion shaft and differential device comprising the same |
| KR101982224B1 (en) * | 2017-06-22 | 2019-05-24 | 주식회사 베어링아트 | Differential device comprising the double row bearing for pinion shaft |
| CN113551019A (en) * | 2020-04-08 | 2021-10-26 | 沃尔沃汽车公司 | Differential assembly |
| CN113551019B (en) * | 2020-04-08 | 2023-10-10 | 沃尔沃汽车公司 | Differential assembly |
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