JPH05332407A - Pinion carrier structure of planetary gear - Google Patents
Pinion carrier structure of planetary gearInfo
- Publication number
- JPH05332407A JPH05332407A JP4144246A JP14424692A JPH05332407A JP H05332407 A JPH05332407 A JP H05332407A JP 4144246 A JP4144246 A JP 4144246A JP 14424692 A JP14424692 A JP 14424692A JP H05332407 A JPH05332407 A JP H05332407A
- Authority
- JP
- Japan
- Prior art keywords
- pinion
- pinion gear
- gear
- pinion carrier
- carrier
- 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
- 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
-
- 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
- F16C19/38—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 two or more rows of rollers
- F16C19/383—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
- F16C19/386—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller 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
- 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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/085—Bearings for orbital gears
-
- 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
- F16H57/08—General details of gearing of gearings with members having orbital motion
-
- 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
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Retarders (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両に搭載される自動
変速機などに組み込まれる遊星歯車装置のピニオンキャ
リア構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pinion carrier structure for a planetary gear unit incorporated in an automatic transmission mounted on a vehicle.
【０００２】[0002]
【従来の技術】従来、遊星歯車装置のピニオンキャリア
構造としては、例えば、実開昭６０−６５４６９号公報
に記載されたものもが知られている。2. Description of the Related Art Conventionally, as a pinion carrier structure of a planetary gear device, for example, one described in Japanese Utility Model Laid-Open No. 60-65469 is known.
【０００３】この従来のピニオンキャリア構造は、ピニ
オンギヤがピニオンシャフトによってピニオンキャリア
に軸支され、ピニオンギヤとピニオンシャフトとの間に
ニードルベアリングが設けられ、ピニオンギヤの端面と
キャリア本体の端面の間にスラスト受けワッシャが介在
された構造となっている。また、ニードルベアリング
は、複数の円柱状のコロが、ピニオンギヤの内周面とピ
ニオンシャフトの外周面の間に介装された構造となって
いる。In this conventional pinion carrier structure, a pinion gear is pivotally supported on a pinion carrier by a pinion shaft, a needle bearing is provided between the pinion gear and the pinion shaft, and a thrust bearing is provided between the end face of the pinion gear and the end face of the carrier body. It has a structure with a washer interposed. Further, the needle bearing has a structure in which a plurality of cylindrical rollers are interposed between the inner peripheral surface of the pinion gear and the outer peripheral surface of the pinion shaft.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、上述の
ような従来の遊星歯車装置のピニオンキャリア構造にあ
っては、ピニオンギヤの回転に伴ってピニオンギヤには
スラスト力が発生し、しかもニードルベアリングには誘
起スラスト力が発生するが、ピニオンシャフトおよびニ
ードルベアリングのコロが円柱状に形成されているた
め、ピニオンギヤやニードルベアリングはピニオンシャ
フトの軸心方向に移動して、ピニオンギヤの端面やニー
ドルベアリングがワッシャに圧接される。これにより、
ピニオンギヤやニードルベアリングやワッシャに磨耗な
どの不都合が起きるという問題点があった。However, in the conventional pinion carrier structure of the planetary gear device as described above, a thrust force is generated in the pinion gear as the pinion gear rotates and is induced in the needle bearing. Although thrust force is generated, since the pinion shaft and needle bearing rollers are formed in a cylindrical shape, the pinion gear and needle bearing move in the axial direction of the pinion shaft, and the end face of the pinion gear and the needle bearing are pressed against the washer. To be done. This allows
There was a problem that the pinion gear, the needle bearing, and the washer suffered inconveniences such as wear.
【０００５】しかも、このようにピニオンギヤやニード
ルベアリングがスラスト方向に移動するのを受ける前記
スラスト受けワッシャは必須の構成部品となり、この分
だけ部品点数が増加していた。Moreover, the thrust receiving washer, which receives the movement of the pinion gear and the needle bearing in the thrust direction, is an indispensable component, and the number of components is increased accordingly.
【０００６】本発明は、上述の問題点に着目して成され
たもので、ピニオンギヤの回転中に起きるピニオンギヤ
およびピニオンキャリアの磨耗などの不都合を解消で
き、しかも、スラスト受けワッシャをなくして部品点数
の削減を図ることができる遊星歯車装置のピニオンキャ
リア構造を提供することを目的としている。The present invention has been made in view of the above-mentioned problems, and it is possible to eliminate inconveniences such as wear of the pinion gear and the pinion carrier that occur during the rotation of the pinion gear, and further, eliminate the thrust receiving washer to reduce the number of parts. It is an object of the present invention to provide a pinion carrier structure of a planetary gear device that can reduce
【０００７】[0007]
【課題を解決するための手段】そこで本発明は、ピニオ
ンギヤとピニオンキャリアとの間にテーパローラベアリ
ングを設けて上述の目的を達成することとした。In view of the above, the present invention achieves the above object by providing a tapered roller bearing between a pinion gear and a pinion carrier.
【０００８】すなわち、本発明の遊星歯車装置のピニオ
ンキャリア構造にあっては、ピニオンキャリアがピニオ
ンギヤを回転自在に支持している遊星歯車装置のピニオ
ンキャリア構造において、前記ピニオンギヤとピニオン
キャリアとの間に、コロの回転中心軸がピニオンギヤの
軸心に対して傾いているとともに、コロの一端側の径と
他端側の径とが異なるテーパベアリングを設けた。That is, in the pinion carrier structure of the planetary gear device of the present invention, in the pinion carrier structure of the planetary gear device in which the pinion carrier rotatably supports the pinion gear, between the pinion gear and the pinion carrier. A tapered bearing is provided in which the center axis of rotation of the roller is inclined with respect to the axis of the pinion gear and the diameter of one end of the roller is different from that of the other end.
【０００９】なお、上述のテーパローラベアリングを設
ける位置は、ピニオンギヤとピニオンキャリアとの間で
あれば、ピニオンギヤとピニオンシャフトとの間や、ピ
ニオンギヤとピニオンキャリアとの間や、ピニオンシャ
フトとピニオンキャリアとの間のいずれに設けてもよ
い。The position where the above-mentioned tapered roller bearing is provided is between the pinion gear and the pinion carrier, between the pinion gear and the pinion shaft, between the pinion gear and the pinion carrier, and between the pinion shaft and the pinion carrier. It may be provided anywhere.
【００１０】[0010]
【作用】ピニオンギヤの回転時には、この回転に伴って
ピニオンギヤにスラスト力が発生するが、ピニオンギヤ
とピニオンキャリアとの間に介在されたテーパローラベ
アリングにより、ピニオンギヤの軸心方向の移動が規制
される。これにより、ピニオンギヤがピニオンキャリア
に圧接されて起きるピニオンギヤおよびピニオンキャリ
アの磨耗などの不都合が解消できるとともに、スラスト
受けワッシャが不要となって部品点数の削減を図ること
ができる。When the pinion gear rotates, a thrust force is generated in the pinion gear due to this rotation, but the taper roller bearing interposed between the pinion gear and the pinion carrier restricts the axial movement of the pinion gear. As a result, it is possible to eliminate inconveniences such as wear of the pinion gear and the pinion carrier caused by the pinion gear being pressed against the pinion carrier, and it is possible to reduce the number of parts by eliminating the thrust receiving washer.
【００１１】[0011]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。Embodiments of the present invention will be described below with reference to the drawings.
【００１２】（第１実施例）まず、実施例の構成につい
て説明する。(First Embodiment) First, the structure of the embodiment will be described.
【００１３】図２は、本発明の第１実施例の遊星歯車装
置のピニオンキャリア構造を備えた自動変速機の要部断
面図であって、本実施例構造を主変速機（図外）と副変
速機Ａとを備えた自動変速機の副変速機Ａに適用してい
る。FIG. 2 is a sectional view of an essential part of an automatic transmission equipped with a pinion carrier structure for a planetary gear device according to a first embodiment of the present invention. The structure of this embodiment is referred to as a main transmission (not shown). It is applied to the auxiliary transmission A of the automatic transmission including the auxiliary transmission A.
【００１４】副変速機Ａは、図外の主変速機からトルク
を入力する入力軸１ａと、外部にトルクを出力する出力
軸１ｂと、所定の変速比が得られる遊星歯車装置２と、
この遊星歯車装置２を構成する回転要素を連結させたり
固定させたりするためのダイレクトクラッチ６およびリ
ダクションブレーキ７とを備えている。The sub-transmission A includes an input shaft 1a for inputting torque from a main transmission (not shown), an output shaft 1b for outputting torque to the outside, and a planetary gear unit 2 for obtaining a predetermined gear ratio.
It is provided with a direct clutch 6 and a reduction brake 7 for connecting and fixing the rotary elements constituting the planetary gear device 2.
【００１５】前記遊星歯車装置２は、入力軸１ａに結合
されたリングギヤ２１と、出力軸１ｂの外周に設けられ
たインナレース８に回転自在に支持されたサンギヤ２３
と、各ギヤ２１，２３に噛合されたピニオンギヤ２２
と、このピニオンギヤ２２を支持していると共に、前記
出力軸１ｂに結合されたピニオンキャリア２４とを有し
ている。The planetary gear device 2 has a ring gear 21 connected to the input shaft 1a and a sun gear 23 rotatably supported by an inner race 8 provided on the outer periphery of the output shaft 1b.
And the pinion gear 22 meshed with each gear 21, 23
And a pinion carrier 24 that supports the pinion gear 22 and is coupled to the output shaft 1b.
【００１６】次に、図１は第１実施例の遊星歯車装置２
におけるピニオンキャリア２４の構造を示す拡大断面図
であって、ピニオンキャリア２４は、ピニオン本体２４
ｂの軸孔２４ｃにピニオンシャフト２４ａを架け渡して
形成されている。そして、ピニオンシャフト２４ａにピ
ニオンギヤ２２が回転自在に支持されている。Next, FIG. 1 shows the planetary gear unit 2 of the first embodiment.
2 is an enlarged cross-sectional view showing the structure of the pinion carrier 24 in FIG.
It is formed by bridging the pinion shaft 24a in the shaft hole 24c of b. The pinion gear 22 is rotatably supported on the pinion shaft 24a.
【００１７】また、ピニオンギヤ２２の内周面の両端部
には、断面円形の陥没部２２ａが形成されており、各陥
没部２２ａの内周面とピニオンシャフト２４ａの外周面
との間には、テーパローラベアリング２５が圧入されて
いる。すなわち、前記テーパローラベアリング２５は、
ピニオンシャフト２４ａの外周に装着されて、外方へ進
むほど大径化した形状のインナレース２５ａと、ピニオ
ンギヤ２２の陥没部２２ａに装着されて、ピニオンギヤ
２２の中央方向へ進むほど大径化した形状のアウタレー
ス２５ｂと、前記インナレース２５ａとアウタレース２
５ｂとの間に介在されて、外方へ進むほど大径化した形
状のテーパローラ（コロ）２５ｃから構成されている。Further, recessed portions 22a having a circular cross section are formed at both ends of the inner peripheral surface of the pinion gear 22, and between the inner peripheral surface of each recessed portion 22a and the outer peripheral surface of the pinion shaft 24a. The taper roller bearing 25 is press-fitted. That is, the taper roller bearing 25 is
The inner race 25a is attached to the outer circumference of the pinion shaft 24a and has a diameter that increases toward the outside, and the shape that is attached to the recess 22a of the pinion gear 22 and that increases toward the center of the pinion gear 22. Outer race 25b, inner race 25a and outer race 2
5b, and a tapered roller (roller) 25c having a diameter increasing toward the outside.
【００１８】次に第１実施例の作用について説明する。Next, the operation of the first embodiment will be described.
【００１９】ピニオンギヤ２２が回転すると、この回転
に伴ってピニオンギヤ２２にスラスト力が発生する。そ
して、このスラスト力によりピニオンギヤ２２が軸方向
（図１左右方向）に移動しようとしても、ピニオンギヤ
２２の軸方向の両端部にはテーパローラベアリング２５
が介在されていて、この軸方向移動は規制される。When the pinion gear 22 rotates, a thrust force is generated in the pinion gear 22 with this rotation. Even if the pinion gear 22 tries to move in the axial direction (left and right direction in FIG. 1) by this thrust force, the tapered roller bearings 25 are provided at both axial end portions of the pinion gear 22.
Is interposed, and this axial movement is restricted.
【００２０】なお、テーパローラ２５ｃとインナレース
２５ａとの接触面やテーパローラ２５ｃとアウタレース
２５ｂとの接触面は、ピニオンシャフト２４ａの軸方向
に対して傾斜しており、従来のニードルベアリングに比
べ、同じスラスト方向長さに対して接触面積が大きくな
って、ＰＶ値が上がる。また、このテーパベアリング２
５の接触角を任意に設定することにより、種々のスラス
ト方向の力やラジアル方向の力のかかり具合に任意に対
応することができる。The contact surface between the taper roller 25c and the inner race 25a and the contact surface between the taper roller 25c and the outer race 25b are inclined with respect to the axial direction of the pinion shaft 24a, which is the same thrust as the conventional needle bearing. The contact area increases with respect to the directional length, and the PV value increases. Also, this taper bearing 2
By arbitrarily setting the contact angle of No. 5, it is possible to arbitrarily deal with various kinds of thrust-direction forces and radial-direction forces.
【００２１】このようにテーパローラベアリング２５に
よりピニオンギヤ２２の移動を規制するため、従来手段
のようにピニオンギヤ２２の端面がキャリア本体２４ｂ
に圧接されることにより起きる磨耗等の不都合を解消で
きると同時に、ピニオンギヤ２２とキャリア本体２４ｂ
との間にスラスト受けワッシャを介装させる必要がなく
なり、このスラスト受けワッシャが不要になって部品点
数の削減を図ることができるという効果が得られる。As described above, since the movement of the pinion gear 22 is restricted by the taper roller bearing 25, the end surface of the pinion gear 22 has the carrier body 24b as in the conventional means.
It is possible to eliminate the inconvenience such as wear caused by being pressed against the pinion gear 22 and the carrier body 24b.
Since it is not necessary to interpose a thrust receiving washer between the above and the above, this thrust receiving washer becomes unnecessary, and the number of parts can be reduced.
【００２２】（第２実施例）図３は、本発明の第２実施
例の遊星歯車装置のピニオンキャリア構造の要部を示す
断面図である。この第２実施例は、ピニオンキャリア２
２４のキャリア本体２２４ｂの内側面に、ピニオンシャ
フトとしての短尺な軸部２２４ｄを一体形成し、この軸
部２２４ｄでピニオンギヤ２２２を支持するとともに、
この軸部２２４ｄの外周面とピニオンギヤ２２２の陥没
部２２ａとの間にテーパローラベアリング２５を設けた
例である。(Second Embodiment) FIG. 3 is a sectional view showing a main part of a pinion carrier structure of a planetary gear device according to a second embodiment of the present invention. This second embodiment is based on the pinion carrier 2
A short shaft part 224d as a pinion shaft is integrally formed on the inner surface of the carrier body 224b of 24, and the shaft part 224d supports the pinion gear 222,
This is an example in which a tapered roller bearing 25 is provided between the outer peripheral surface of the shaft portion 224d and the depressed portion 22a of the pinion gear 222.
【００２３】なお、ピニオンギヤ２２２は、第１実施例
のピニオンシャフト２４ａを貫通させる貫通孔が形成さ
れていないが、第１実施例のピニオンギヤ２２を用いる
こともできる。Although the pinion gear 222 is not formed with a through hole for penetrating the pinion shaft 24a of the first embodiment, the pinion gear 22 of the first embodiment may be used.
【００２４】以上のように第２実施例では、キャリア本
体２２４ｂの内側面にピニオンシャフト２４ａの代わり
となる軸部２２４ｄを一体形成したので、ピニオンシャ
フト２４ａを省略して部品点数をさらに削減できる。な
お、その他の構成および作用は第１実施例と同様である
ため説明を省略する。As described above, in the second embodiment, since the shaft portion 224d which replaces the pinion shaft 24a is integrally formed on the inner surface of the carrier body 224b, the pinion shaft 24a can be omitted to further reduce the number of parts. The rest of the configuration and operation are the same as in the first embodiment, so a description thereof will be omitted.
【００２５】（第３実施例）図４は、本発明の第３実施
例の遊星歯車装置のピニオンキャリア構造の要部を示す
断面図である。この第３実施例は、ピニオンシャフト２
４ａをピニオンギヤ２２２に固着し、また、ピニオンキ
ャリア３２４のキャリア本体３２４ｂの軸孔３２４ｃを
大径化して、この軸孔２２４ｃとピニオンシャフト２４
ａの外周面との間にテーパローラベアリング３２５を設
けたものである。この第３実施例のテーパローラベアリ
ング３２５は、外方へ進むほど小径化した形状のインナ
レース３２５ａと、逆にピニオンギヤ３２２方向へ進む
ほど小径化した形状のアウタレース３２５ｂおよびテー
パローラ３２５ｃが装着された構造のもので、また、ピ
ニオンギヤ３２２には、第１，２実施例の陥没部２２ａ
が形成されていない。なお、その他の構成および作用は
第１実施例と同様であるため説明を省略する。(Third Embodiment) FIG. 4 is a sectional view showing a main part of a pinion carrier structure of a planetary gear device according to a third embodiment of the present invention. In this third embodiment, the pinion shaft 2
4a is fixed to the pinion gear 222, and the diameter of the shaft hole 324c of the carrier body 324b of the pinion carrier 324 is increased so that the shaft hole 224c and the pinion shaft 24
A tapered roller bearing 325 is provided between the outer peripheral surface of a and a. The taper roller bearing 325 of the third embodiment has a structure in which an inner race 325a having a smaller diameter toward the outside, and an outer race 325b and a taper roller 325c having a smaller diameter toward the pinion gear 322 are mounted. The pinion gear 322 has a recess 22a of the first and second embodiments.
Is not formed. The rest of the configuration and operation are similar to those of the first embodiment, so the description thereof will be omitted.
【００２６】（第４実施例）図５は、本発明の第４実施
例の遊星歯車装置のピニオンキャリア構造の要部を示す
断面図である。この第４実施例は、ピニオンキャリア４
２４のキャリア本体４２４ｂにすり鉢形の陥没部４２４
ｅを形成し、一方、ピニオンギヤ４２２の両端の中央部
に、前記陥没部４２４ｅに符合した先細り形状の軸部４
２２ｂを一体形成し、さらに、陥没部４２４ｅをアウタ
レースとするとともに、軸部４２２ｂをインナレースと
し、かつ、両者間にテーパローラ３２５ｃを有したテー
パローラベアリング４２５設けたものである。(Fourth Embodiment) FIG. 5 is a sectional view showing an essential part of a pinion carrier structure of a planetary gear device according to a fourth embodiment of the present invention. The fourth embodiment is based on the pinion carrier 4
24 carrier bodies 424b with mortar-shaped depressions 424
On the other hand, at the center of both ends of the pinion gear 422, the tapered shaft portion 4 corresponding to the recessed portion 424e is formed.
22b is integrally formed, the recessed portion 424e is an outer race, the shaft portion 422b is an inner race, and a taper roller bearing 425 having a taper roller 325c is provided between them.
【００２７】以上のように、この第４実施例にあって
は、ワッシャ，ピニオンシャフトを省略した上、さら
に、テーパローラベアリングのアウタレースおよびイン
ナレースを省略しているため、部品点数をよりいっそう
削減できる。なお、その他の構成および作用は第３実施
例と同様であるため説明を省略する。As described above, in the fourth embodiment, the washer and the pinion shaft are omitted, and the outer race and the inner race of the taper roller bearing are omitted, so that the number of parts is further reduced. it can. The rest of the configuration and operation are the same as in the third embodiment, so a description thereof will be omitted.
【００２８】（第５実施例）図６は、本発明の第５実施
例の遊星歯車装置のピニオンキャリア構造の要部を示す
断面図である。この第５実施例は、ピニオンキャリア５
２４における図中左側のキャリア本体５２４ｂの軸孔５
２４ｃを大径に形成し、図中右側のキャリア本体５２４
ｂの軸孔５２４ｃを小径に形成し、ピニオンギヤ５２２
の内周をテーパ形状に形成し、さらに、ピニオンシャフ
ト５２４ａとピニオンギヤ５２２との間に、第１のテー
パローラベアリング５２５と第２のテーパローラベアリ
ング５２６とを設けたものである。(Fifth Embodiment) FIG. 6 is a sectional view showing an essential part of a pinion carrier structure of a planetary gear device according to a fifth embodiment of the present invention. In this fifth embodiment, the pinion carrier 5 is used.
24, the shaft hole 5 of the carrier body 524b on the left side in the drawing.
24c is formed in a large diameter, and the carrier body 524 on the right side in the drawing
The shaft hole 524c of b is formed in a small diameter, and the pinion gear 522 is
The inner circumference is formed in a taper shape, and further, a first taper roller bearing 525 and a second taper roller bearing 526 are provided between the pinion shaft 524a and the pinion gear 522.
【００２９】なお、ピニオンシャフト５２４ａは、図中
左側半分の大径部５２４ｆと、図中右側半分の小径部５
２４ｇとで形成している。そして、大径部５２４３ｆ
は、図中右側端部が先細り形状に形成され、一方、小径
部は、全体に亘り同一径に形成されている。The pinion shaft 524a has a large diameter portion 524f on the left side in the figure and a small diameter portion 5 on the right side in the figure.
It is formed with 24 g. And the large diameter portion 5243f
In the drawing, the right end portion in the drawing is formed in a tapered shape, while the small diameter portion is formed to have the same diameter throughout.
【００３０】また、第１のテーパローラベアリング５２
５は、小径部２４ｇの外周にインナレース２５ａを設
け、ピニオンギヤ５２２の内周をアウタレースとし、両
者の間にテーパローラ５２５ｃを設けて構成している。Also, the first taper roller bearing 52
In No. 5, the inner race 25a is provided on the outer circumference of the small diameter portion 24g, the inner circumference of the pinion gear 522 is the outer race, and the taper roller 525c is provided between the two.
【００３１】一方、第２のテーパローラベアリング５２
６は、大径部５２４ｆの外周のテーパ状部分をインナレ
ースとする一方、ピニオンギヤ５２２の内周のテーパ状
部分をアウタレースとし、両者の間にテーパローラ２５
ｃを設けて構成している。On the other hand, the second taper roller bearing 52
In No. 6, the tapered portion on the outer circumference of the large diameter portion 524f is the inner race, while the tapered portion on the inner circumference of the pinion gear 522 is the outer race, and the tapered roller 25
It is configured by providing c.
【００３２】第５実施例におけるピニオンギヤ２２の組
み付け手順の一例を説明すると、まず、一方のキャリア
本体５２４ｂにピニオンシャフト５２４ａの大径部５２
４ｆを嵌合させ、次に、間にテーパローラ５２５ｃを介
在させながら大径部５２４ｆにピニオンギヤ５２２を装
着し、次いで、小径部５２４ｇとピニオンギヤ５２２と
の間にインナレース２５ａおよびテーパローラ５２５ｃ
を装着し、その後、小径部５２４ｇを他方のキャリア本
体５２４ｂの小径側の軸孔５２４ｃに嵌合させて組み付
けを終える。An example of the assembling procedure of the pinion gear 22 in the fifth embodiment will be described. First, the large diameter portion 52 of the pinion shaft 524a is attached to one carrier body 524b.
4f is fitted, and then the pinion gear 522 is attached to the large diameter portion 524f with the taper roller 525c interposed therebetween, and then the inner race 25a and the taper roller 525c are interposed between the small diameter portion 524g and the pinion gear 522.
After that, the small diameter portion 524g is fitted into the shaft hole 524c on the small diameter side of the other carrier body 524b to complete the assembly.
【００３３】なお、他の構成および作用は第１実施例と
同様であるため説明を省略する。The rest of the configuration and operation are the same as in the first embodiment, so a description thereof will be omitted.
【００３４】（第６実施例）図７は、本発明の第６実施
例の遊星歯車装置のピニオンキャリア構造の要部を示す
断面図である。この第６実施例は、ピニオンシャフト６
２４ａを２つの分割シャフト６２４ｈを連結して構成
し、両者にテーパ部６２４ｉを形成し、ピニオンギヤ５
２２とピニオンシャフト６２４ａとの間に、テーパロー
ラベアリング６２５を設けている。なお、テーパローラ
ベアリング６２５は、テーパ部６２４ｉをインナレース
とするとともにピニオンギヤ５２２の内周をアウタレー
スとし、両者の間にテーパローラ２５ｃを設けて構成し
ている。(Sixth Embodiment) FIG. 7 is a sectional view showing an essential part of a pinion carrier structure of a planetary gear device according to a sixth embodiment of the present invention. In this sixth embodiment, the pinion shaft 6
24a is formed by connecting two split shafts 624h, and a taper portion 624i is formed on both shafts.
A tapered roller bearing 625 is provided between the No. 22 and the pinion shaft 624a. The taper roller bearing 625 is configured such that the taper portion 624i is an inner race, the inner circumference of the pinion gear 522 is an outer race, and the taper roller 25c is provided therebetween.
【００３５】第６実施例におけるピニオンギヤ２２の組
み付け手順の一例を説明すると、まず、一方のキャリア
本体２４ｂの貫通孔２４ｃに一方の分割シャフト６２４
ｈを嵌合させ、間にテーパローラ２５ｃを介在させなが
らこの一方の分割シャフト６２４ｈにピニオンギヤ５２
２を装着する。次いで、他方の分割シャフト６２４ｈを
一方の分割シャフト６２４ｈに結合させると同時に、こ
の他方の分割シャフト６２４ｈとピニオンギヤ５２２と
の間にテーパローラ２５ｃを装着する。An example of an assembling procedure of the pinion gear 22 in the sixth embodiment will be described. First, one split shaft 624 is inserted into the through hole 24c of the one carrier body 24b.
h is fitted to the pinion gear 52 while the tapered roller 25c is interposed therebetween.
Wear 2. Next, the other split shaft 624h is coupled to the one split shaft 624h, and at the same time, the taper roller 25c is mounted between the other split shaft 624h and the pinion gear 522.
【００３６】なお、他の構成および作用は第１実施例と
同様であるため説明を省略する。The rest of the configuration and operation are the same as in the first embodiment, so a description thereof will be omitted.
【００３７】以上、本発明の実施例を図面により説明し
てきたが、具体的な構成はこの実施例に限られるもので
はなく、本発明の要旨を逸脱しない範囲の設計変更等が
あっても本発明に含まれる。The embodiment of the present invention has been described above with reference to the drawings. However, the specific structure is not limited to this embodiment, and the present invention can be applied even if there is a design change or the like within the scope not departing from the gist of the present invention. Included in the invention.
【００３８】例えば、実施例では、本発明のピニオンキ
ャリア構造を有した遊星歯車装置を自動変速機に適用し
た例を示したが、適用範囲は自動変速機に限られず、他
の産業機器に適用してもよい。For example, in the embodiment, the example in which the planetary gear device having the pinion carrier structure of the present invention is applied to the automatic transmission is shown, but the applicable range is not limited to the automatic transmission and is applied to other industrial equipment. You may.
【００３９】[0039]
【発明の効果】以上説明したように、本発明の遊星歯車
装置のピニオンキャリア構造にあっては、ピニオンギヤ
とピニオンキャリアとの間に、テーパローラベアリング
を設けた構成としたため、テーパローラベアリングによ
りピニオンギヤのスラスト方向の移動が規制されること
になり、ピニオンギヤの端面がピニオンキャリアに圧接
されることにより起きるピニオンギヤおよびピニオンキ
ャリアの磨耗といった不都合を解消することができると
ともに、従来手段において必須構成部品であったピニオ
ンギヤとピニオンキャリアとの間に介在するスラスト受
けワッシャが不要になって部品点数の削減を図ることが
できるという効果が得られる。As described above, in the pinion carrier structure of the planetary gear device of the present invention, since the tapered roller bearing is provided between the pinion gear and the pinion carrier, the pinion gear is formed by the tapered roller bearing. Since the movement of the pinion gear in the thrust direction is restricted, the disadvantages such as wear of the pinion gear and the pinion carrier caused by the end face of the pinion gear being pressed against the pinion carrier can be eliminated, and it is an essential component in the conventional means. Further, the thrust receiving washer that is interposed between the pinion gear and the pinion carrier is not required, and the number of parts can be reduced.
【図１】本発明の第１実施例の遊星歯車装置のピニオン
キャリア構造を適用した副変速機を示す断面図である。FIG. 1 is a sectional view showing an auxiliary transmission to which a pinion carrier structure of a planetary gear device according to a first embodiment of the present invention is applied.
【図２】本発明の第１実施例ピニオンキャリア構造の要
部を示す断面図である。FIG. 2 is a sectional view showing a main part of a pinion carrier structure according to a first embodiment of the present invention.
【図３】本発明の第２実施例の遊星歯車装置のピニオン
キャリア構造の要部を示す断面図である。FIG. 3 is a sectional view showing a main part of a pinion carrier structure of a planetary gear device according to a second embodiment of the present invention.
【図４】本発明の第３実施例の遊星歯車装置のピニオン
キャリア構造の要部を示す断面図である。FIG. 4 is a sectional view showing a main part of a pinion carrier structure of a planetary gear device according to a third embodiment of the present invention.
【図５】本発明の第４実施例の遊星歯車装置のピニオン
キャリア構造の要部を示す断面図である。FIG. 5 is a sectional view showing a main part of a pinion carrier structure of a planetary gear device according to a fourth embodiment of the present invention.
【図６】本発明の第５実施例の遊星歯車装置のピニオン
キャリア構造の要部を示す断面図である。FIG. 6 is a sectional view showing a main part of a pinion carrier structure of a planetary gear device according to a fifth embodiment of the present invention.
【図７】本発明の第６実施例の遊星歯車装置のピニオン
キャリア構造の要部を示す断面図である。FIG. 7 is a sectional view showing a main part of a pinion carrier structure of a planetary gear device according to a sixth embodiment of the present invention.
２ 遊星歯車装置 ２２ ピニオンギヤ ２２２ ピニオンギヤ ３２２ ピニオンギヤ ４２２ ピニオンギヤ ５２２ ピニオンギヤ ２４ ピニオンキャリア ２２４ ピニオンキャリア ３２４ ピニオンキャリア ４２４ ピニオンキャリア ５２４ ピニオンキャリア ６２４ ピニオンキャリア ２５ テーパローラベアリング ３２５ テーパローラベアリング ４２５ テーパローラベアリング ５２５ テーパローラベアリング ５２６ テーパローラベアリング ６２５ テーパローラベアリング ２５ｃ テーパローラ（コロ） ３２５ｃ テーパローラ（コロ） ４２５ｃ テーパローラ（コロ） ５２５ｃ テーパローラ（コロ） 2 Planetary gear device 22 Pinion gear 222 Pinion gear 322 Pinion gear 422 Pinion gear 522 Pinion gear 24 Pinion carrier 224 Pinion carrier 324 Pinion carrier 424 Pinion carrier 524 Pinion carrier 624 Pinion carrier 25 25 Tapered roller bearing 5 25 Tapered roller bearing 5 25 Tapered roller bearing 5 25 Tapered roller bearing 5 25 Roller bearing 625 Tapered roller bearing 25c Tapered roller (roller) 325c Tapered roller (roller) 425c Tapered roller (roller) 525c Tapered roller (roller)
Claims (1)
自在に支持している遊星歯車装置のピニオンキャリア構
造において、 前記ピニオンギヤとピニオンキャリアとの間に、コロの
回転中心軸がピニオンギヤの軸心に対して傾いていると
ともに、コロの一端側の径と他端側の径とが異なるテー
パベアリングを設けたことを特徴とする遊星歯車装置の
ピニオンキャリア構造。1. A pinion carrier structure of a planetary gear device in which a pinion carrier rotatably supports a pinion gear, wherein a center axis of rotation of a roller is inclined with respect to an axis of the pinion gear between the pinion gear and the pinion carrier. In addition, the pinion carrier structure of the planetary gear device is characterized in that a taper bearing having different diameters on one end side and the other end side of the rollers is provided.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4144246A JPH05332407A (en) | 1992-06-04 | 1992-06-04 | Pinion carrier structure of planetary gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4144246A JPH05332407A (en) | 1992-06-04 | 1992-06-04 | Pinion carrier structure of planetary gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05332407A true JPH05332407A (en) | 1993-12-14 |
Family
ID=15357642
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4144246A Pending JPH05332407A (en) | 1992-06-04 | 1992-06-04 | Pinion carrier structure of planetary gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH05332407A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100451908B1 (en) * | 2000-03-08 | 2004-10-15 | 임광철 | Input gear protection apparatus of reduction gear |
| US7056259B2 (en) * | 2001-06-28 | 2006-06-06 | The Timken Company | Epicyclic gear system |
| JP2008232314A (en) * | 2007-03-22 | 2008-10-02 | Ntn Corp | Tapered roller bearing for planet rotor |
| JP2009174589A (en) * | 2008-01-22 | 2009-08-06 | Nsk Ltd | Planetary gear type transmission, continuously variable transmission and assembling method of planetary gear type transmission |
| EP2187096A3 (en) * | 2008-11-14 | 2011-09-07 | Sankyo Seisakusho Co. | Planetary rolling rotation transmission device |
| WO2012114847A1 (en) * | 2011-02-24 | 2012-08-30 | Ntn株式会社 | Planetary gear device |
| WO2012160887A1 (en) * | 2011-05-20 | 2012-11-29 | Ntn株式会社 | Reduction differential gear apparatus for electric vehicle |
| WO2016023761A1 (en) * | 2014-08-12 | 2016-02-18 | Robert Bosch Gmbh | Hand-held machine tool gear unit |
| EP3486523A1 (en) * | 2017-11-17 | 2019-05-22 | IMS Gear SE & Co. KGaA | Planetary carrier |
-
1992
- 1992-06-04 JP JP4144246A patent/JPH05332407A/en active Pending
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100451908B1 (en) * | 2000-03-08 | 2004-10-15 | 임광철 | Input gear protection apparatus of reduction gear |
| US7056259B2 (en) * | 2001-06-28 | 2006-06-06 | The Timken Company | Epicyclic gear system |
| JP2008232314A (en) * | 2007-03-22 | 2008-10-02 | Ntn Corp | Tapered roller bearing for planet rotor |
| JP2009174589A (en) * | 2008-01-22 | 2009-08-06 | Nsk Ltd | Planetary gear type transmission, continuously variable transmission and assembling method of planetary gear type transmission |
| EP2187096A3 (en) * | 2008-11-14 | 2011-09-07 | Sankyo Seisakusho Co. | Planetary rolling rotation transmission device |
| JP2012189202A (en) * | 2011-02-24 | 2012-10-04 | Ntn Corp | Planetary gear device |
| WO2012114847A1 (en) * | 2011-02-24 | 2012-08-30 | Ntn株式会社 | Planetary gear device |
| WO2012160887A1 (en) * | 2011-05-20 | 2012-11-29 | Ntn株式会社 | Reduction differential gear apparatus for electric vehicle |
| CN103547836A (en) * | 2011-05-20 | 2014-01-29 | Ntn株式会社 | Reduction differential gear apparatus for electric vehicle |
| US8968139B2 (en) | 2011-05-20 | 2015-03-03 | Ntn Corporation | Reduction differential gear apparatus for electric vehicle |
| WO2016023761A1 (en) * | 2014-08-12 | 2016-02-18 | Robert Bosch Gmbh | Hand-held machine tool gear unit |
| US11181186B2 (en) | 2014-08-12 | 2021-11-23 | Robert Bosch Gmbh | Handheld power tool gearbox unit |
| EP3486523A1 (en) * | 2017-11-17 | 2019-05-22 | IMS Gear SE & Co. KGaA | Planetary carrier |
| US10634239B2 (en) | 2017-11-17 | 2020-04-28 | Ims Gear Se & Co. Kgaa | Planet carrier for supporting at least one planet wheel in a planetary gear for an adjustment unit for adjusting two components adjustable in relation to one another, planetary gear comprising such a planet carrier, and motor-gear unit comprising such a planetary gear |
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