JPS61184257A - Planetary gear device - Google Patents
Planetary gear deviceInfo
- Publication number
- JPS61184257A JPS61184257A JP60021949A JP2194985A JPS61184257A JP S61184257 A JPS61184257 A JP S61184257A JP 60021949 A JP60021949 A JP 60021949A JP 2194985 A JP2194985 A JP 2194985A JP S61184257 A JPS61184257 A JP S61184257A
- Authority
- JP
- Japan
- Prior art keywords
- planetary gear
- stage
- unit
- planet carrier
- gear unit
- 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.)
- Granted
Links
Landscapes
- Structure Of Transmissions (AREA)
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
、〔発明の利用分□野〕
本発明は多段式の遊星歯車変速装置に関するもので）る
。DETAILED DESCRIPTION OF THE INVENTION Field of Application of the Invention The present invention relates to a multi-stage planetary gear transmission.
〔発明の背景〕 ゛例□えば電
動式リモートコントロールミラー、電動格納式アウトサ
イドミラー等の自動車用付属機器において、動力源であ
る電動機の回転用゛力を減速伝動しなければならない場
合が多い。こうした場合、小形、軽量で比較的大きい変
速比を得るには遊星歯車式の減速機が適している。[Background of the Invention] For example, in automobile accessories such as electric remote control mirrors and electric retractable outside mirrors, it is often necessary to reduce and transmit the rotational force of the electric motor that is the power source. In such cases, a planetary gear type speed reducer is suitable for obtaining a relatively large speed ratio while being compact and lightweight.
しかし、遊星歯車による１段減速では減速比が一−−−
−−−頁
充分でないときは多段式の遊星歯車装置が用いられる。However, in the one-stage reduction using planetary gears, the reduction ratio is 1 ----
---If there are not enough pages, a multi-stage planetary gear system is used.
第５図は従来用いられている多段遊星歯車変速機の１例
として示した３段遊星歯車式減速機の縦断面図である。FIG. 5 is a longitudinal cross-sectional view of a three-stage planetary gear reduction gear shown as an example of a conventionally used multi-stage planetary gear transmission.
円筒状のケーシング−内に、これと同心状に３組の遊星
歯車ユニツ）Ｐ□＋Ｐ２＋Ｐ３が収納されている。Three sets of planetary gear units) P□+P2+P3 are housed concentrically within the cylindrical casing.
Ｐｌは第１段減速用遊星歯車ユニットで、そのサンギヤ
は入力軸２に接続されている。この第１段減速遊星歯車
ユニツ）Ｐ□のプラネットキャリヤは次段Ｐ２のサンギ
ヤに連結されている。このようにして各段の遊星歯車ユ
ニットはその出力をプラネットキャリヤから次段のサン
ギヤに伝え、最終段の遊星歯車ユニットＰ３のプラネッ
トキャリヤは出力軸３に連結される。上に述べた各段の
遊星歯車ユニットのリングギヤは円筒状ケース１に収納
され、通しボルト４で固定されている。Pl is a first-stage reduction planetary gear unit, and its sun gear is connected to the input shaft 2. The planet carrier of this first stage reduction planetary gear unit) P□ is connected to the sun gear of the next stage P2. In this way, the planetary gear unit at each stage transmits its output from the planet carrier to the sun gear at the next stage, and the planet carrier of the planetary gear unit P3 at the final stage is connected to the output shaft 3. The ring gears of the planetary gear units at each stage described above are housed in a cylindrical case 1 and fixed with through bolts 4.
本例（第４図）に示したように、各段の遊星歯車ユニッ
トは、従来一般に構成部品の共通化を図特開昭Ｇ１−１
８４２５７（２）
す、歯車の主要諸元（各歯車同志の径、歯数、モジュー
ル等）が同様に揃えられてイル。As shown in this example (Fig. 4), the planetary gear units of each stage were conventionally made to have common components.
84257 (2) The main specifications of the gears (diameter of each gear, number of teeth, module, etc.) are aligned in the same way.
以上のように構成された従来の遊星歯車式変速装置（第
５図）は、減速機としても増速機としても用いることが
できるが、
（ａ） 各減速段は、後段に近いほどトルクが増大さ
れるにも拘らず、各段の容量が同様であるため不合理で
、装置全体が大形、大重量になること。The conventional planetary gear type transmission (Fig. 5) configured as described above can be used both as a speed reducer and a speed increaser. Despite the increased capacity, the capacity of each stage remains the same, which is unreasonable, resulting in the overall size and weight of the device.
（ｂ） 構成部品点数が多く、組立工数が大きいこと
。(b) The number of component parts is large and the number of assembly steps is large.
といった不具合が有る。There are some problems.
本発明は上述の事情に鑑みて為されたもので、各段の遊
星歯車ユニット毎に容量を適正に配分して装置全体を小
形、１＃、量に構成することができ。The present invention has been made in view of the above-mentioned circumstances, and the capacity can be appropriately distributed to each planetary gear unit at each stage, thereby making it possible to configure the entire device into a compact device with a size of 1#.
構造が簡単で組立所要工数の少ない多段遊星歯車式の変
速装置を提供しようとするものである。The object of the present invention is to provide a multi-stage planetary gear type transmission that has a simple structure and requires less man-hours for assembly.
上記の目的を達成する為、本発明の遊星歯車装置は、複
数の遊星歯車ユニットを筒状ケーシング内に同心状に多
段に配列して各遊星歯車ユニット−−−−−−」−−−
−−−頁
のリングギヤをケーシングに対して固定し、配列された
遊星歯車ユニット中の１端悼位置する遊星歯車ユニット
のサンギヤを入力軸に連結するとともにそのユニットの
プラネットキャリヤを次段の遊星歯車ユニットのサンギ
ヤに連結し、各段の遊星歯車ユニットの回転出力を上、
記と同様にして次段の遊星歯車ユニットに伝動し、最終
段の遊星歯車ユニットのプラネットキャリヤを出力軸に
連結して多段遊星歯車式減速機を栴成し、上記の多段遊
星歯車式減速機の入、出力方向を逆転せしめて多段遊星
歯車式増速機としても使用し得べく為したる遊星歯車式
の変速装置において、前記複数組の遊星歯車ユニットは
配列の順にそれぞれ容量の異なるものとし、各遊星歯車
ユニットのリングギヤを筒状ケーシング内に同心状に相
互に離間せしめて設置するとともに、該筒状ケーシング
に設けた複数個のリングギヤの間に凹形の円柱面を設け
、かつ、各遊星歯車、ユニットのプラネットキャリヤの
外周を円柱面状に構成し、該円柱面状の外周部のそれぞ
れを前記凹形円柱面に対してそれぞれ摺−９−−−−−
一頁
動自在に嵌合せしめ、プラネットキャリヤの軸心をリン
グギヤの軸心に一致せしめて回転自在に支承したことを
特徴とする。In order to achieve the above object, the planetary gear device of the present invention has a plurality of planetary gear units arranged concentrically in multiple stages in a cylindrical casing, so that each planetary gear unit
The ring gear on page ---- is fixed to the casing, the sun gear of the planetary gear unit located at one end of the arranged planetary gear units is connected to the input shaft, and the planet carrier of that unit is connected to the planetary gear of the next stage. Connected to the unit's sun gear, the rotational output of each stage of the planetary gear unit is increased.
In the same manner as described above, the power is transmitted to the next stage planetary gear unit, and the planet carrier of the final stage planetary gear unit is connected to the output shaft to form a multistage planetary gear type reducer. In a planetary gear type transmission which can be used as a multi-stage planetary gear type speed increaser by reversing input and output directions, the plurality of sets of planetary gear units have different capacities in the order of arrangement. , the ring gears of each planetary gear unit are installed concentrically and spaced apart from each other in a cylindrical casing, and a concave cylindrical surface is provided between the plurality of ring gears provided in the cylindrical casing, and each The outer periphery of the planet carrier of the planetary gear and unit is formed into a cylindrical surface, and each of the cylindrical outer peripheries slides against the concave cylindrical surface.
The planet carrier is fitted so as to be freely movable, and the axis of the planet carrier is aligned with the axis of the ring gear, and the planet carrier is rotatably supported.
次に１本発明の１実施例を第１図乃至第４図について説
明する。Next, one embodiment of the present invention will be described with reference to FIGS. 1 to 4.
第１図は第２図の１−１断面図、第２図は第１図のｌｌ
−１断面図、第３図は分解斜視図である。Figure 1 is a 1-1 sectional view of Figure 2, Figure 2 is ll of Figure 1.
-1 sectional view and FIG. 3 are exploded perspective views.
第１図は前述の従来例における第５図に対応する図であ
って、第５図の図面参照番号にダラシを付して示した円
筒状ケーシング１／、入力軸２′、出力軸３′はそれぞ
れ従来例における構成部材に対応する部材である。FIG. 1 is a diagram corresponding to FIG. 5 in the conventional example described above, and the drawing reference numbers in FIG. are members corresponding to the constituent members in the conventional example.
本実施例においては、円筒状ケーシングｌ′内に４組の
遊星歯車ユニツｔ’Ｑｔ〜Ｑ４を配列しである。In this embodiment, four sets of planetary gear units t'Qt to Q4 are arranged in a cylindrical casing l'.
上記各遊星歯車ユニットの内でＱ□は第１段減速用Ｑ２
は第２段減速、用、ＱＢは第３段減速用ｂ Ｑ４は第４
段（最終段）減速用の遊星歯車ユニットである。Among the above planetary gear units, Q□ is for Q2 for first stage reduction.
is for 2nd stage reduction, QB is for 3rd stage reduction, Q4 is for 4th stage reduction.
This is a planetary gear unit for stage (final stage) reduction.
減速段の順に伝達トルクが大きくなるので、前記４組の
減速ユニツ） Ｑｔ〜Ｑ４はＴｈ Ｑｔ〜Ｑ４の順に漸
一−−−−−−−−−頁
次大容量の遊星歯車機構を構成してあル、本第１図に表
わされているように歯幅、軸径、及び歯車径が順次に大
きくなっている。Since the transmitted torque increases in the order of the reduction stage, the four sets of reduction units) Qt to Q4 gradually form a planetary gear mechanism with a large capacity. As shown in FIG. 1, the tooth width, shaft diameter, and gear diameter gradually increase.
第１図に示したように筒状のケーシングｌ′はテーパ筒
状に構成し、その中に４組の遊星歯車ユニットＱ□〜Ｑ
４を組みこんで蓋状のホルダ５で覆い、上輪６で押さえ
である。上記の上輪６を取部外して内部の歯車機構を抜
き出した状態を第４図に示す。１３はケーシング位置決
め・回シ止め用ノックピンである。As shown in Fig. 1, the cylindrical casing l' has a tapered cylindrical shape, and four sets of planetary gear units Q□ to Q
4 is assembled, covered with a lid-like holder 5, and held down with an upper ring 6. FIG. 4 shows a state in which the upper wheel 6 is removed and the internal gear mechanism is extracted. 13 is a dowel pin for positioning and locking the casing.
第１段〜第４段の遊星歯車ユニットのリングギヤ７−１
〜７−４は筒状ケーシングｌ′と一体に構成してアル、
各段の遊星歯車ユニットのサンギヤ８−□〜８−４、各
段のプラネットギヤ９−１〜９−４、および各段のプラ
ネットキャリヤ１０−０〜１０−４が抜き出される。Ring gear 7-1 of the 1st to 4th stage planetary gear units
~7-4 is constructed integrally with the cylindrical casing l',
The sun gears 8-□ to 8-4 of the planetary gear units at each stage, the planet gears 9-1 to 9-4 at each stage, and the planet carriers 10-0 to 10-4 at each stage are extracted.
１２−□〜１２−４は座金状のスペーサである。12-□ to 12-4 are washer-shaped spacers.
前述の如く各段の遊星歯車ユニットは終減速段に近づく
につれて順次に容量を大きく構成しであるので、４個の
リングギヤ７−□〜７−４は順次に大径となシ、これら
を一体に連設した筒状ケーシング１′の内面は多段の凹
形円柱面状をなしている。そして、各段のリングギヤ７
−１〜７−４を互いに軸心方向に離間せしめて設けると
ともに、これらリングギヤ７−０〜７−４それぞれの終
減速段側（図において左側）にリングギヤの歯底円とほ
ぼ等径の凹形円柱面１１−０〜１１−４を設ける。As mentioned above, the planetary gear units at each stage have their capacities increased in sequence as they approach the final reduction stage, so the four ring gears 7-□ to 7-4 have successively larger diameters, and are integrated into one unit. The inner surface of the cylindrical casing 1' connected to the cylindrical casing 1' has a multi-stage concave cylindrical surface shape. And the ring gear 7 of each stage
-1 to 7-4 are provided spaced apart from each other in the axial direction, and each of these ring gears 7-0 to 7-4 has a concave portion on the final reduction stage side (left side in the figure) having a diameter approximately equal to the root circle of the ring gear. Cylindrical surfaces 11-0 to 11-4 are provided.
そして、前記のプラネットキャリヤ１０−１〜１０−４
の外周面は、それぞれ前記凹形円柱面１１−□〜１１−
４と摺動自在に嵌合する円柱面状に構成する。これによ
シプラネットキャリャはリングギヤに対して同心状にか
つ回転自在に支承される。And the planet carriers 10-1 to 10-4
The outer peripheral surfaces of the concave cylindrical surfaces 11-□ to 11- are respectively
4 and has a cylindrical shape that is slidably fitted. Thereby, the shipplanet carrier is supported concentrically and rotatably with respect to the ring gear.
以上のように構成した遊星歯車装置を組み立てる場合は
、第４図に示すごとく各段の遊星歯車ユニットの構成部
材の内でリングギヤを除く部分を仮組みして、これを筒
状ケーシングｌ′の中に挿入し、第１図に示したように
上輪６を嵌着すると組立作業が完了するので、組立が迅
速、容易である。When assembling the planetary gear device configured as described above, as shown in Fig. 4, the parts of the planetary gear unit of each stage except for the ring gear are temporarily assembled, and then this is assembled into the cylindrical casing l'. Assembling is completed by inserting it inside and fitting the upper ring 6 as shown in FIG. 1, so assembly is quick and easy.
特に、多段の遊星歯車ユニットを１段ずつケーシング内
に組みつけてゆく操作を必要としないので組立所要工数
が少ない。In particular, since it is not necessary to assemble the multi-stage planetary gear unit into the casing one stage at a time, the number of man-hours required for assembly is reduced.
一−−−−−−−−−−−−頁
その上、各減速段の遊星歯車ユニットの容量をそれぞれ
適正に設定しであるので、最終段においても充分な強度
を有し、しかも初段１次段は不必要な強度を有していな
いので、装置全体の強度分布がバランスしていて、その
結果、装置全体が小形軽量である上に、装置全体として
の信頼性、耐久性が優れている。In addition, since the capacity of the planetary gear unit of each reduction stage is set appropriately, the final stage has sufficient strength, and the first stage Since the next stage does not have unnecessary strength, the strength distribution of the entire device is balanced, and as a result, the entire device is small and lightweight, and the device as a whole has excellent reliability and durability. There is.
以上詳述したように５本発明の遊星歯車装置は装置全体
が小形、軽量であってしかも信頼性、耐久性が優れてお
シ、その上、構造が簡単で組立所要工数が少ないという
優れた実用的効果を奏する。As detailed above, the planetary gear device of the present invention is compact and lightweight as a whole, and has excellent reliability and durability.Furthermore, it has a simple structure and requires less man-hours for assembly. It has practical effects.
第１図は本発明の１実施例における縦断面図で、第２図
の１−１面による切断面を描いである。
第２図は第１図のｌ−Ｈ断面図、第３図は前記実施例の
分解斜視図、第４図は同じく分解断面図である。
第５図は従来形の多段遊星歯車式変速機の１例の部分断
面図である。
−４０−頁
１．１′・・・円筒状ケーシング、 ２．２’・・・
入力軸、３．３′・・・出力軸、７−０〜７−２・・・
リングギヤ、８−０〜８−４・・・サンギヤ、９−１〜
９−４・・・プラネットギヤ、１０−４〜１Ｏ−４・・
・プラネットキャリヤ、１１−０〜１１−４・・・凹形
円柱面、１２−□〜１２イ・・座金状スペーサ。FIG. 1 is a longitudinal cross-sectional view of one embodiment of the present invention, taken along the plane 1--1 of FIG. 2. 2 is a sectional view taken along the line l-H in FIG. 1, FIG. 3 is an exploded perspective view of the embodiment, and FIG. 4 is an exploded sectional view. FIG. 5 is a partial sectional view of an example of a conventional multi-stage planetary gear transmission. -40- Page 1.1'...Cylindrical casing, 2.2'...
Input shaft, 3.3'... Output shaft, 7-0 to 7-2...
Ring gear, 8-0~8-4...Sun gear, 9-1~
9-4...Planet gear, 10-4~1O-4...
- Planet carrier, 11-0 to 11-4... Concave cylindrical surface, 12-□ to 12i... Washer-shaped spacer.
Claims (1)
に多段に配列し、各遊星歯車ユニットのリングギヤをケ
ーシングに対して固定し、配列された遊星歯車ユニット
中の１端に位置する遊星歯車ユニットのサンギヤを入力
軸に連結するとともにそのユニットのプラネットキャリ
ヤを次段の遊星歯車ユニットのサンギヤに連結し、各段
の遊星歯車ユニットの回転出力を上記と同様にして次段
の遊星歯車ユニットに伝動し、最終段の遊星歯車ユニッ
トのプラネットキャリヤを出力軸に連結して多段遊星歯
車式減速機を構成し、上記の多段遊星歯車式減速機の入
、出力方向を逆転せしめたとき遊星歯車式増速機として
も使用し得べく為したる遊星歯車式の変速装置において
、前記複数組の遊星歯車ユニットは配列の順にそれぞれ
容量の異なるものとし、各遊星歯車ユニットのリングギ
ヤを筒状ケーシング内に同心状に相互に離間せしめて設
置するとともに、該筒状ケーシングに設けた複数個のリ
ングギヤの間に凹形の円柱面を設け、かつ、各遊星歯車
ユニットのプラネットキャリヤの外周を円柱面状に構成
し、該円柱面状の外周部のそれぞれを前記凹形円柱面に
対してそれぞれ摺動自在に嵌合せしめ、該プラネットキ
ャリヤの軸心をリングギヤの軸心に一致せしめて回転自
在に支承したことを特徴とする多段式の遊星歯車装置。A planetary gear unit in which a plurality of sets of planetary gear units are arranged concentrically in multiple stages within a cylindrical casing, a ring gear of each planetary gear unit is fixed to the casing, and the planetary gear unit is located at one end of the arranged planetary gear units. The sun gear of the unit is connected to the input shaft, and the planet carrier of that unit is connected to the sun gear of the planetary gear unit of the next stage, and the rotational output of the planetary gear unit of each stage is transmitted to the planetary gear unit of the next stage in the same manner as above. The planet carrier of the final stage planetary gear unit is connected to the output shaft to form a multi-stage planetary gear type reducer, and when the input and output directions of the multi-stage planetary gear type reducer are reversed, the planetary gear type In a planetary gear type transmission that can also be used as a speed gear, the plurality of planetary gear units have different capacities in the order of arrangement, and the ring gear of each planetary gear unit is arranged concentrically within a cylindrical casing. A concave cylindrical surface is provided between the plurality of ring gears provided in the cylindrical casing, and the outer periphery of the planet carrier of each planetary gear unit is formed into a cylindrical surface shape. and each of the cylindrical surface-shaped outer peripheral portions is slidably fitted to the concave cylindrical surface, and the planet carrier is rotatably supported with its axis aligned with the axis of the ring gear. A multi-stage planetary gear device featuring:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60021949A JPH071056B2 (en) | 1985-02-08 | 1985-02-08 | Planetary gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60021949A JPH071056B2 (en) | 1985-02-08 | 1985-02-08 | Planetary gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61184257A true JPS61184257A (en) | 1986-08-16 |
| JPH071056B2 JPH071056B2 (en) | 1995-01-11 |
Family
ID=12069311
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60021949A Expired - Lifetime JPH071056B2 (en) | 1985-02-08 | 1985-02-08 | Planetary gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH071056B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH029352U (en) * | 1988-06-30 | 1990-01-22 | ||
| JP4834070B2 (en) * | 2005-03-11 | 2011-12-07 | エクスラー アクチエンゲゼルシャフト | Electric motor brake actuator |
| KR101449423B1 (en) * | 2012-10-25 | 2014-10-15 | (주)프로테크코리아 | Pipe fixing apparatus |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101326764B1 (en) * | 2013-04-03 | 2013-11-08 | 재단법인차세대융합기술연구원 | Transmission |
| JP7374791B2 (en) | 2020-01-31 | 2023-11-07 | マブチモーター株式会社 | Reducer and geared motor |
-
1985
- 1985-02-08 JP JP60021949A patent/JPH071056B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH029352U (en) * | 1988-06-30 | 1990-01-22 | ||
| JP4834070B2 (en) * | 2005-03-11 | 2011-12-07 | エクスラー アクチエンゲゼルシャフト | Electric motor brake actuator |
| KR101449423B1 (en) * | 2012-10-25 | 2014-10-15 | (주)프로테크코리아 | Pipe fixing apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH071056B2 (en) | 1995-01-11 |
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