JPS60227041A - Driving device - Google Patents
Driving deviceInfo
- Publication number
- JPS60227041A JPS60227041A JP8182284A JP8182284A JPS60227041A JP S60227041 A JPS60227041 A JP S60227041A JP 8182284 A JP8182284 A JP 8182284A JP 8182284 A JP8182284 A JP 8182284A JP S60227041 A JPS60227041 A JP S60227041A
- Authority
- JP
- Japan
- Prior art keywords
- arm
- support pin
- hole
- support
- 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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
- F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
- F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
- F02N15/043—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer
- F02N15/046—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer of the planetary type
-
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、遊星歯車機構を設けた駆動装置に係１１Ｍ３
ｒ−ニーＨ／Ｆ％＊ｎ＊＝；ｊｋｌｌｌｔ−Ｌ／’−−
ｂ％ノア７％ｒ−−’１ｍｙｊｄｋｋｌ−Ｊ−５同軸状
に配設しであるリダ同軸状ンスタータに関する。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a drive device equipped with a planetary gear mechanism.
r-knee H/F%*n*=;jkllllt-L/'--
b% Noah 7% r--'1myjdkkl-J-5 Concerning a coaxial starter that is coaxially arranged.
自動車用内燃機関の駆動装置として実開昭５８−７５９
５７号公報に、遊星歯機構を備えたりダクションスター
タが開示されている。このリダクションスタータは、モ
ータの回転軸とピニオンの回転軸とを同軸状に配設し、
実開昭４９−１３０２３７号公報に開示されている平歯
車減速装置に用いた。いわゆる二軸リダクションスター
タに対して大幅な小型を図るものである。リダクション
スタータの遊星歯車機構は、遊星歯車の支持ピンをピニ
オン軸と一体に形成した遊星腕の孔に圧入し、固定して
いる。Used as a drive device for internal combustion engines for automobiles in 1987-759
No. 57 discloses a duction starter equipped with a planetary tooth mechanism. This reduction starter has the rotation axis of the motor and the rotation axis of the pinion coaxially arranged,
It was used in a spur gear reduction device disclosed in Japanese Utility Model Application Publication No. 49-130237. It is intended to be significantly smaller than a so-called two-shaft reduction starter. In a planetary gear mechanism of a reduction starter, a support pin of a planetary gear is press-fitted into a hole in a planetary arm formed integrally with a pinion shaft and fixed therein.
しかし、第１図に示す如く遊星腕１ｏに固定した支持ピ
ン１２，１４，１６の回転中心Ｑに対する取付は寸法が
１例えばｒｌ ｌ ｙ ｒａｐ ｒ３（７）ようになっ
た場合１機関始動の際の過大な衝撃力が最大河転半径ｒ
３を有する支持ピン１６−に支持された遊星歯車に加わ
る。そして−子のＥｆｌが古坊ビン１６に作用するため
、支持ビンの孔への圧入力が不十分な場合、支持ビンが
緩んだり、抜は出たりし、遊星歯車の正常な噛合いを阻
害する。このため、従来は支持ビンの圧入部の長さを必
要以上に長くしており、スタータの軸方向が長くなる欠
点を有していた。また、取イ１寸法を精度良くそろえる
ためには、相当のコストを必要とし、自動車用スタータ
として採用できない欠点があった。However, as shown in Fig. 1, when the support pins 12, 14, and 16 fixed to the planetary arm 1o are attached to the rotation center Q, when the dimensions are 1, for example, rl l y rap r3 (7), when starting one engine. The excessive impact force causes the maximum drift radius r
It joins a planetary gear supported by a support pin 16- having a diameter of 3. Since the second Efl acts on the old pin 16, if the pressing force into the hole in the support pin is insufficient, the support pin will loosen or come out, which will prevent the normal meshing of the planetary gear. do. For this reason, in the past, the length of the press-fitted part of the support bottle was made longer than necessary, which had the disadvantage that the starter became longer in the axial direction. Furthermore, in order to precisely align the dimensions of each groove, a considerable amount of cost is required, which has the disadvantage that it cannot be used as a starter for automobiles.
本発明は、軸方向の１１法を短かくすることができる遊
星歯車（後横を備えた駆動装置を提供することを目的と
する。SUMMARY OF THE INVENTION An object of the present invention is to provide a drive device equipped with a planetary gear (rear side) that can shorten the length of the gear in the axial direction.
本発明は、遊星歯車を回転自在に支持する支持ビンに周
溝を形成し、支持ビンの周溝の部分を出力軸に設けた腕
の孔に挿入し、この腕の孔の周囲を挿圧して塑性流動を
生起させて前記周溝に流入させ、支持ビンと腕との間に
緊迫力を発生させ、支持ビンと腕どを強固に結合するこ
とにより、支持ビンの孔への挿入長さを短かくして装置
の軸方向寸法を短かくできるように構成したものである
。In the present invention, a circumferential groove is formed in a support bin that rotatably supports a planetary gear, the circumferential groove part of the support bin is inserted into a hole in an arm provided on an output shaft, and pressure is applied around the hole in the arm. This causes plastic flow to flow into the circumferential groove, generates a tension force between the support bottle and the arm, and firmly connects the support bottle and the arm, thereby increasing the insertion length of the support bottle into the hole. The structure is such that the axial dimension of the device can be shortened by shortening the length.
本発明に係る駆動装置に好ましい実施例を、添付図面に
従って詳説する。Preferred embodiments of the drive device according to the present invention will be described in detail with reference to the accompanying drawings.
第２図は、本発明に係る駆動装置の実施例の断面図であ
る。第２図において、モータ１８は、電機子２０が入力
軸である軸２２に取り付けられ、軸受２４，２６を介し
てリヤカバー２８内に回転自在に支持されている。軸２
２は、一端に中心太陽歯車である電機子ビニオン３０が
形成されている。電機子ピニオン３０の周囲には軸２２
と同軸に内歯リング歯車３２が配設しである。そして、
電機子ピニオン３０と内歯リング歯車３２とが形成する
環状空間３４には、遊星歯車３６が複数個（例えば３個
）等間隔をもって配置しである。遊星歯車３６は、例え
ばニードルベアリング等を介して支持ビン３８に回転自
在に支持され、それぞれ電機子ピニオン３０と内歯リン
グ歯車３２とに噛合っている。FIG. 2 is a sectional view of an embodiment of the drive device according to the invention. In FIG. 2, the motor 18 has an armature 20 attached to a shaft 22 serving as an input shaft, and is rotatably supported within a rear cover 28 via bearings 24 and 26. Axis 2
2 has an armature binion 30, which is a central sun gear, formed at one end. Around the armature pinion 30 is a shaft 22.
An internal ring gear 32 is disposed coaxially with. and,
In an annular space 34 formed by the armature pinion 30 and the internal ring gear 32, a plurality (for example, three) of planetary gears 36 are arranged at equal intervals. The planetary gear 36 is rotatably supported by a support pin 38 via, for example, a needle bearing, and meshes with the armature pinion 30 and the internal ring gear 32, respectively.
支持ビン３８は、詳細を後述するととくピニオン軸４
＋）の一端に設けた遊星腕４２に固定されている。ピニ
オン軸４０は、軸受４／Ｉ、４６を介し′Ｃセンターブ
ラケット４８とギヤケース５０とに回転自在に支持され
、中間部周囲にはビニオン５２が配設されている。さら
に、ピニオン軸４０の周囲には、ピニオン軸４０の回転
をビニオン５２に伝達するローラクラッチ５４と、ビニ
オン５２を軸方向に移動させるクラッチスリーブ５６と
が設けである。The support pin 38 is attached to the pinion shaft 4, the details of which will be described later.
+) is fixed to a planetary arm 42 provided at one end. The pinion shaft 40 is rotatably supported by a 'C center bracket 48 and a gear case 50 via bearings 4/I and 46, and a pinion 52 is disposed around the intermediate portion. Further, around the pinion shaft 40, there are provided a roller clutch 54 that transmits the rotation of the pinion shaft 40 to the pinion 52, and a clutch sleeve 56 that moves the pinion 52 in the axial direction.
ギヤケース５０内に設けたシフトレバ−５８は、一端が
ギヤケース５０に固定したマグネッ１−スイッチ６０と
結合しており、他端がクラッチスリーブ５６の溝部６２
に嵌入している。また、ギヤケース５０には、固定ボル
ト６４を介してリヤカバー２８と、電機子２０の周囲に
配設するヨーク６６とが固定しである。The shift lever 58 provided inside the gear case 50 has one end connected to a magnetic switch 60 fixed to the gear case 50, and the other end connected to a groove 62 of the clutch sleeve 56.
It is embedded in Further, a rear cover 28 and a yoke 66 disposed around the armature 20 are fixed to the gear case 50 via fixing bolts 64.
遊星腕４２は、第３図に示す如くピニオン軸４０の一端
にピニオン軸４ｏと一体に形成されている。そして、′
Ｍ遊星腕２には、有底の結合孔６８が設けられ、この結
合孔６８に支持ビン３８の一端が挿入され、固定しであ
る７支持ビン３８の結合孔６８に挿入した部分の外周面
には、第４図に示すごとく略Ｗ字状をなす結合溝７０が
周方向に形成しである。The planetary arm 42 is formed integrally with the pinion shaft 4o at one end of the pinion shaft 40, as shown in FIG. and,'
The M planetary arm 2 is provided with a bottomed coupling hole 68, one end of the support bottle 38 is inserted into this coupling hole 68, and the outer peripheral surface of the part inserted into the coupling hole 68 of the fixed 7 support bottle 38 is As shown in FIG. 4, a substantially W-shaped coupling groove 70 is formed in the circumferential direction.
支持ビン３８と遊星１１５ｉ！４２との結合は、遊星腕
４２に塑性流動を生起させることにより行なわれる。即
ち、結合溝６８に支持ビン３８の結合溝７０を形成した
部分を挿入し、結合溝６８の周囲を凸状の金型をもつ′
Ｃ押圧してリング状の四部７２を形成する。すると、遊
星腕４２を構成する部材が塑性流動を起こして結合溝７
０内に流入し。Support bin 38 and planet 115i! The coupling with the planetary arm 42 is performed by causing plastic flow in the planetary arm 42. That is, the part of the support bottle 38 in which the coupling groove 70 is formed is inserted into the coupling groove 68, and the periphery of the coupling groove 68 is surrounded by a convex mold.
Press C to form ring-shaped four parts 72. Then, the members constituting the planetary arm 42 cause plastic flow and the coupling groove 7
Flow into 0.
支持ビン３８と遊星腕４２との間に大きな緊迫力が発生
し、両者がこの緊迫力により結合する。A large tension force is generated between the support bin 38 and the planetary arm 42, and the two are coupled together by this tension force.
この実施例の作用は、次のとおりである。The operation of this embodiment is as follows.
モータ１８に電力が供給されると、電機子２０に１−ル
クが発生し回転する。電機子２０の回転により、軸２２
が電機子２０と一体に回転し、この回転が電機子ピニオ
ン３０．内歯リング歯車３２゜遊星歯車３６からなる遊
星歯車機構を介して、ピニオン軸４０に所定の減速比を
もって伝達され、ピニオン軸が大きな１〜ルクをもって
回転する。ピニオン軸４０の回転は、スプライン及びロ
ーラ７ラツチ５４を介してピニオン５２に伝達される。When electric power is supplied to the motor 18, 1-lux is generated in the armature 20, causing it to rotate. Due to the rotation of the armature 20, the shaft 22
rotates integrally with armature 20, and this rotation causes armature pinion 30. It is transmitted to the pinion shaft 40 at a predetermined reduction ratio through a planetary gear mechanism consisting of an internal ring gear 32° and a planetary gear 36, and the pinion shaft rotates with a large torque of 1 to 1. Rotation of pinion shaft 40 is transmitted to pinion 52 via spline and roller 7 latch 54.
方、モータ■８ノ＼の供電と同時にマグネットノ、イツ
チ６０にも供電され、マグネツ１−スイッチ６０が作動
してシフトレバ−５８の第２図における。」二端部を左
方向に移動させる。このため、シフＩ〜レバー５８の一
ド端部は、クラッチスリーブ５６を介してピニオン５２
を右方向に移動させ、ピニオン５２の回転が図示しない
内燃機関のリングギヤに伝達するように、ピニオン５２
と内燃機関のリングギヤとを噛合せる。On the other hand, when power is supplied to the motor 8, power is also supplied to the magnet switch 60, and the magnet 1 switch 60 is actuated to shift the shift lever 58 to the position shown in FIG. ” Move the second end to the left. Therefore, one end of the shift I lever 58 is connected to the pinion 52 through the clutch sleeve 56.
The pinion 52 is moved to the right so that the rotation of the pinion 52 is transmitted to the ring gear of the internal combustion engine (not shown).
and the ring gear of the internal combustion engine.
この際、第１図に示した如く複数の支持ビン３８の回転
中心０に対する取付寸法に多少の不整があったどしても
、支持ビン３８どｊｌｉ 奥院４２とは大きな緊迫力を
もって結合しているため、支持ビン３８の緩み：３８の
緩みや抜けを牛しる二どがない。At this time, even if there is some irregularity in the mounting dimensions of the plurality of support bins 38 with respect to the rotation center 0 as shown in FIG. Therefore, there is no way to know if the support bottle 38 is loose or has come loose.
第５図及び第６図は、支持ビンと遊星腕どの結合構造の
他の実施例を示したものである。木実施例においては、
結合孔６８が貫通穴となっており、この結合孔６８の両
端周縁部を押圧してリング状の凹部７２．７４が形成し
である。、このようにすることにより −四人きな結合
１）を得ることができる。5 and 6 show other embodiments of the coupling structure between the support bin and the planet arm. In the tree embodiment,
The coupling hole 68 is a through hole, and ring-shaped recesses 72 and 74 are formed by pressing the peripheral edges of both ends of the coupling hole 68. , By doing this, we can obtain -four-person combination 1).
なお、前記実施例においては、結合１．７０がＷ字状で
ある場合について説明したが、Ｖ字状の結合溝であって
も大きな結合力を得ることができる。In the above embodiment, the case where the bond 1.70 is W-shaped has been described, but even if the bond groove is V-shaped, a large bonding force can be obtained.
また、Ｗ溝の中央部の山にローレットを形成することに
より、回転トルクに対する強度を増すことができる。Furthermore, by forming a knurling on the crest at the center of the W groove, the strength against rotational torque can be increased.
以」−説明したように、本発明によれば支持ビンと遊星
腕は結合力を高めることにより、支持ビンの腕への挿入
部を短かくでき、装置の軸方向寸法を小さくすることが
できる。As described above, according to the present invention, by increasing the bonding force between the support bottle and the planetary arm, the insertion portion of the support bottle into the arm can be shortened, and the axial dimension of the device can be reduced. .
第１図は）Ｗ星歯車を支持する支持ビンの取付状態を示
す説明図、第２図は本発明に係る駆動装置の実施例の断
面図、第３図はピニオン軸の一部を断面にした詳細図、
第４図は支持ビンと遊星腕との結合構造の詳細を示す断
面図、第５図及び第６図は支持ビンと遊星腕との結合構
造の他の実施例を示す図である。
Ｉ８・・・モータ、２０−・電機子、シ：２・・Φ・−
１００電機子ピニオン、３２・・内歯リーノグ歯屯、二
目；・″ｔｉ星歯車、３８・支持ビン、４０・・・ピニ
オン軸、４２−・）Ｗ爪腕、１）８−・・結合孔、７０
−・結合溝、代理人 弁理士 高橋明夫
＄１ 固
第３日
第４図
第５図
第６図
にｇFig. 1 is an explanatory diagram showing the mounting state of the support bin that supports the W star gear, Fig. 2 is a sectional view of an embodiment of the drive device according to the present invention, and Fig. 3 is a sectional view of a part of the pinion shaft. detailed diagram,
FIG. 4 is a cross-sectional view showing details of the coupling structure between the support bottle and the planetary arm, and FIGS. 5 and 6 are views showing other embodiments of the coupling structure between the support bottle and the planetary arm. I8...Motor, 20-・Armature, C:2...Φ・-
100 armature pinion, 32...internal gear nog tooth, second; ``ti star gear, 38, support pin, 40... pinion shaft, 42-) W claw arm, 1) 8-... combination Hole, 70
-・Connection groove, agent Patent attorney Akio Takahashi $1 3rd day, figure 4, figure 5, figure 6 g
Claims (1)
囲に同軸的に配設されたリング両軸と、このリング両軸
と前記中心太陽歯車とが形成する環状空間に設けた遊星
歯車と、この遊星歯車の回転に伴い回転する出力軸と、
この出力軸に形成した腕に固定され、前記遊星歯車を回
転自在に支持している支持ピンとを有する駆動装置にお
いて、前記出力軸の腕に形成した前記支持ピンを挿入す
る結合孔と、前記支持ピンの結合孔に挿入される部分に
形成した周溝とが設けられ、この周溝に塑性流動した前
記腕を構成する部材が流入して、前記支持ピンと前記腕
との間に生じた緊迫力により結合していることを特徴ど
する駆動装置、1. An input shaft having a central sun gear, both ring shafts coaxially arranged around the four central sun gears, and a planetary gear provided in an annular space formed by the ring shafts and the central sun gear. , an output shaft that rotates as the planetary gear rotates,
In a drive device having a support pin fixed to an arm formed on the output shaft and rotatably supporting the planetary gear, a coupling hole formed on the arm of the output shaft into which the support pin is inserted; A circumferential groove is formed in the portion of the pin that is inserted into the coupling hole, and the plastically fluid member constituting the arm flows into the circumferential groove, thereby reducing the tension force generated between the support pin and the arm. a drive device characterized in that it is coupled by a
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8182284A JPS60227041A (en) | 1984-04-25 | 1984-04-25 | Driving device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8182284A JPS60227041A (en) | 1984-04-25 | 1984-04-25 | Driving device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60227041A true JPS60227041A (en) | 1985-11-12 |
Family
ID=13757174
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8182284A Pending JPS60227041A (en) | 1984-04-25 | 1984-04-25 | Driving device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60227041A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62188310U (en) * | 1986-05-23 | 1987-11-30 | ||
| JPH0169183U (en) * | 1987-10-28 | 1989-05-08 | ||
| US5382203A (en) * | 1993-04-01 | 1995-01-17 | Ford Motor Company | Planetary gearset carrier assembly |
| KR20180104223A (en) * | 2017-03-09 | 2018-09-20 | 발레오전장시스템스코리아 주식회사 | start motor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51111564A (en) * | 1975-03-26 | 1976-10-01 | Hitachi Ltd | Geared arm of hoist |
| JPS58207510A (en) * | 1982-05-27 | 1983-12-03 | 豊生ブレ−キ工業株式会社 | Method of fixing axial material to tabular material |
-
1984
- 1984-04-25 JP JP8182284A patent/JPS60227041A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51111564A (en) * | 1975-03-26 | 1976-10-01 | Hitachi Ltd | Geared arm of hoist |
| JPS58207510A (en) * | 1982-05-27 | 1983-12-03 | 豊生ブレ−キ工業株式会社 | Method of fixing axial material to tabular material |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62188310U (en) * | 1986-05-23 | 1987-11-30 | ||
| JPH0169183U (en) * | 1987-10-28 | 1989-05-08 | ||
| US5382203A (en) * | 1993-04-01 | 1995-01-17 | Ford Motor Company | Planetary gearset carrier assembly |
| KR20180104223A (en) * | 2017-03-09 | 2018-09-20 | 발레오전장시스템스코리아 주식회사 | start motor |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP3490416B2 (en) | Vehicle | |
| KR20060050708A (en) | Driveshaft assembly with torque ring coupling | |
| CN106090039A (en) | The power transmission structure of vehicle | |
| US4573364A (en) | Gear reduction starter drive | |
| JPH04185207A (en) | Wheel motor with reduction gear | |
| WO2009053662A1 (en) | Electric machine comprising an elastic connection to a gearbox primary shaft | |
| JPS60227041A (en) | Driving device | |
| US11703114B2 (en) | Differential gearbox | |
| JP2002089664A (en) | Gear supporting structure and hybrid drive device using it | |
| JP2021132435A (en) | Vehicular driving device | |
| JP4262353B2 (en) | Ring gear | |
| JP3550818B2 (en) | Starter | |
| CN107709811B (en) | Speed changer with torsional vibration damper | |
| CN110081152A (en) | Electric axle for a motor vehicle | |
| JP2017517427A (en) | Vehicle power transmission device (PTU) with planetary gear set | |
| CN110537039B (en) | Transmission for a motor vehicle | |
| CN206419141U (en) | A kind of little gear of starter stir controlling organization and apply its starter | |
| TWI798915B (en) | Electric vehicle two-speed powertrain | |
| JP2975164B2 (en) | Bearing structure of automatic transmission | |
| JPS62251523A (en) | Method of connecting revolving shaft | |
| JP2022094666A (en) | Planetary gear mechanism and manufacturing method of the same | |
| JPS6332420Y2 (en) | ||
| JPH01169152A (en) | Driving gear | |
| JPS61223353A (en) | Planetary reduction type reduction starter | |
| JP2004517276A (en) | Angle drive with annular housing |