JPS61211559A - Star-type planetary gear - Google Patents
Star-type planetary gearInfo
- Publication number
- JPS61211559A JPS61211559A JP4840085A JP4840085A JPS61211559A JP S61211559 A JPS61211559 A JP S61211559A JP 4840085 A JP4840085 A JP 4840085A JP 4840085 A JP4840085 A JP 4840085A JP S61211559 A JPS61211559 A JP S61211559A
- Authority
- JP
- Japan
- Prior art keywords
- planetary
- planetary gear
- gear
- star
- outer casing
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
- F16H1/2836—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planets relative to the planet carrier or by using free floating planets
Landscapes
- Gear Transmission (AREA)
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は主iこ舶用中速ディーゼル機関等の変速に用
いられるスター型遊星歯車装置に関するもので、特に装
置内の変動トルクを有効に吸収できるようにするもので
ある。[Detailed Description of the Invention] [Field of Industrial Application] This invention relates to a star-type planetary gear device mainly used for shifting speeds of medium-speed marine diesel engines, etc., and particularly to a star-type planetary gear device that effectively absorbs fluctuating torque within the device. It is something that makes it possible.
従来、舶用主機(エンジン)として中速ディーゼル機関
を使用する場合、主機の変動トルクを吸収し、増速、減
速等の変速を行なう歯車装置の歯車を保護する目的で、
主機と歯車装置の間Iこ弾性継手を装備するのが一般的
である。一方、機関室をコンパクトにしようとする目的
から、トータルジエンジン長さの長い中速ディーゼル機
関ではコンパクトなプラネタリ−型の遊星変速機等の歯
車装置が用いられ、更に咳プラネタリー型遊星歯車装置
内に別程の変動トルク吸収機構を内蔵させ、上記弾性継
手を用いず主機と該歯車装置とを直結させる提案がなさ
れている。即ち、第2図に示すように、バランスビン(
SOO)と呼ばれる棒状体の両端を内歯車(6ン幅方向
両端部に固定すると共に、その中央部を内歯車(6)外
周に周設された外部ケーシング(2)に固定せしめるこ
とにより、該バランスピン(500)で内歯車(6)を
外部ケーシング(2)に弾性支持せしめ、前記主機から
伝達される変動トルクを吸収せしめる構造をとるもので
ある。Conventionally, when a medium-speed diesel engine is used as a marine main engine (engine), the purpose of absorbing the fluctuating torque of the main engine and protecting the gears of the gear system that performs speed changes such as speed increase and deceleration is
It is common to have an elastic joint between the main engine and the gear. On the other hand, for the purpose of making the engine room more compact, medium-speed diesel engines with long total engine lengths use compact planetary-type planetary transmissions and other gear systems, and even cough planetary-type planetary gear systems. A proposal has been made to incorporate a separate fluctuating torque absorption mechanism inside the engine and directly connect the main engine and the gear device without using the elastic joint. That is, as shown in Figure 2, the balance bin (
By fixing both ends of a rod-shaped body called SOO to both ends in the width direction of the internal gear (6), and fixing the center part to the external casing (2) provided around the outer periphery of the internal gear (6), The internal gear (6) is elastically supported by the external casing (2) by a balance pin (500), and the structure is such that fluctuating torque transmitted from the main engine is absorbed.
しかし、このような技術はプラネタリ−屋遊星歯車装置
に限り有効であり、同じく変速機等として用いられるス
ター屋遊星歯車装置では、その構造上、上記バランスピ
ン(soo) ヲ変動トルク吸収用に用いることができ
ない。However, such technology is only effective for planetary planetary gears, and in star planetary gears that are also used as transmissions, due to their structure, the balance pin (soo) is used to absorb fluctuating torque. I can't.
即ち、外部ケーシング(2Jに固定された内歯車(6)
内で遊星歯車(3)が公転するプラネタリ−製遊星歯車
装置と異なり、スター型遊星歯車装置では第3図)こ示
すように遊星歯車(3)の遊星軸(3a)を支持する固
定板(1)がこれに接する外部ケーシング(2)に固定
支持されているため、該遊星歯車(3)自身は自転でき
ても内歯車(6)内での公転はできず、そのかわり内歯
車(6)をその回りで回転させて太陽歯車(7)の軸(
7a)と内歯車軸(6&)との間で変速する構造である
。従って前記バランスピン(SOO)は回転する内歯車
(6)と外部ケーシング(2)の間に設けることは構造
上不可能であり、又、固定板(1)とこれを固定する外
部ケーシング(2)との間lこ設けることができたとし
ても、有効に変動トルク吸収を行なうことは不可能であ
る。That is, the internal gear (6) fixed to the external casing (2J
Unlike planetary planetary gears in which the planetary gear (3) revolves, star type planetary gears have a fixed plate (3a) that supports the planetary shaft (3a) of the planetary gear (3) as shown in Figure 3). 1) is fixedly supported by the external casing (2) in contact with it, so even though the planetary gear (3) itself can rotate, it cannot revolve within the internal gear (6). ) around it to rotate the sun gear (7) axis (
7a) and the internal gear shaft (6&). Therefore, it is structurally impossible to install the balance pin (SOO) between the rotating internal gear (6) and the external casing (2), and also between the fixed plate (1) and the external casing (2) that fixes it. ), it is impossible to effectively absorb the fluctuating torque.
更に、上記バランスピン(SOO)は、その構造的制約
(例えばその設置位置から考えて轟然太さ・長さに関す
る寸法・形状等の制限や装備できる数の制限があると考
えられる)から損すバネ剛さを小さく出来ないため、こ
れによる変動トルク吸収効果は前記弾性継手より劣り、
トルク変動の大きな機関では、バランスピン(SOO)
のみによる変動トルク吸収でに充分でなく、フライホイ
ール効果の利用や太陽歯車(7)、遊里歯車(3)及び
内歯車(6)の歯面強度アップを行なわねばならない欠
点がある。又、バランスピン(500)の場合、高度の
加工精度が要求されることになる。Furthermore, the above-mentioned balance pin (SOO) is susceptible to damage due to its structural limitations (for example, considering its installation position, there are limitations on dimensions and shapes regarding thickness and length, and limitations on the number of devices that can be equipped). Since the spring stiffness cannot be made small, the effect of absorbing fluctuating torque is inferior to that of the above-mentioned elastic joint.
In engines with large torque fluctuations, the balance pin (SOO)
There is a drawback that it is not sufficient to absorb the fluctuating torque by only using the flywheel effect or to increase the strength of the tooth surfaces of the sun gear (7), the idling gear (3), and the internal gear (6). Further, in the case of the balance pin (500), a high degree of processing accuracy is required.
本発明は上記問題を解決するためなされたもので、プラ
ネタリ−型に適用されたバランスピンの弾性支持に代わ
る技術により上記遊星軸を外部ケーシングに弾性支持し
、製造上の簡便さ及びスター型遊星歯車装置における変
動トルク吸収の向上を達成せんとするものである。The present invention has been made to solve the above problem, and the planetary shaft is elastically supported on the outer casing by a technique that replaces the elastic support of the balance pin applied to the planetary type, thereby simplifying manufacturing and supporting the star type planetary. The objective is to improve the absorption of fluctuating torque in a gear device.
以上本発明の構成を詳述すると、スター型遊星歯車装置
の遊星歯車の遊星軸を、外部ケーシング壁面に取付けた
複数の弾性支持体で夫々支持することlこより、該弾性
支持体の弾性力で上記遊星軸を外部ケーシングに弾性支
持するようにしたものである。To explain the configuration of the present invention in detail above, the planetary shaft of the planetary gear of the star type planetary gear device is supported by a plurality of elastic supports attached to the wall surface of the external casing. The planetary shaft is elastically supported by the outer casing.
このうち弾性支持体とは、コイルバネ、皿バネ等で構成
されるもので、本発明では1の遊星軸に対し、複数方向
からこれに直交するように取付けられて、該遊星軸を外
部ケーシングに弾性支持することにより、太陽歯車や内
歯車から遊星歯車に伝わってくる振動をその弾性力で吸
収するものである。Among these, the elastic support is composed of a coil spring, a disc spring, etc., and in the present invention, it is attached to one planetary shaft from multiple directions perpendicularly thereto, and the elastic support is attached to the outer casing to connect the planetary shaft to the outer casing. By providing elastic support, vibrations transmitted from the sun gear and internal gear to the planetary gear can be absorbed by the elastic force.
本発明は、スター型遊星歯車装置における遊星歯車の弾
性支持構造を、バランスピンに代えて弾性支持体により
構成し、このような構造変更で遊星軸を弾性支持体で支
持しているため、該弾性支持体の仕様を変えることによ
り、前記バランスピンの場合と異なり、より広範囲の捩
りバネ剛さの選択が可能になる。In the present invention, the elastic support structure of the planetary gear in a star type planetary gear device is constructed with an elastic supporter instead of a balance pin, and the planetary shaft is supported by the elastic supporter with such a structural change. By changing the specifications of the elastic support, it is possible to select a wider range of torsion spring stiffnesses, unlike in the case of the balance pin.
即ち、弾性支持体の弾性力によりフライホイール効果の
利用や歯面強度アップを図らないでも大きな変動トルク
を吸収することが可能lこなる。That is, the elastic force of the elastic support makes it possible to absorb a large fluctuating torque without utilizing the flywheel effect or increasing the tooth surface strength.
第1図(a) (b)は本発明の一実施例を示しており
、同図(fL)に示すようにスター壓遊星減速機の遊星
歯車(31(3)は回転する太陽歯車(7)と内歯車(
6)との間Iこ自転可能jこ設けられている。本実施例
では、外部ケーシング(2)の縦壁面(2a)内側に円
環状内面突起■翰が設けられ、その内部中心に前記遊星
歯車(3) (3)の遊星軸(3a)(3a)が延出し
ている。そして同図(a)のA−A断面である(b)に
示すように、円環状内面突起(7)内側百には、弾性支
持体(4) (4) (41の一端が夫々3点に分けて
取付けられており、又、これらの他端はその中心方向で
円環体(5)に取付けられている。この円環体(5)の
中空部lこ前記遊星軸(3a)が挿入されている。即ち
、遊星軸(3a)は上記円環体(5)を介して3方向か
ら延びる弾性支持体(4) (4) (43により支持
されている。FIGS. 1(a) and 1(b) show an embodiment of the present invention, and as shown in FIG. ) and internal gear (
6) A rotatable space is provided between the two. In this embodiment, an annular inner surface projection (2) is provided on the inside of the vertical wall surface (2a) of the external casing (2), and the planetary shaft (3a) (3a) of the planetary gear (3) (3) is located at the center of the inner surface of the ring. is extending. As shown in (b), which is the A-A cross section of the same figure (a), on the inner side of the annular inner protrusion (7), one end of each of the elastic supports (4) (4) (41) is attached at three points. The other end of these is attached to a torus (5) in the direction of its center.The hollow part of this torus (5) is located where the planetary shaft (3a) is located. That is, the planetary shaft (3a) is supported by elastic supports (4) (4) (43) extending from three directions via the toric body (5).
尚、本実施例では第1図(a) iこ示すようEこ、遊
星軸(3a) (3a)を補強板αOに回転可能に成人
せしめており、このような補強板αOlこより上記遊星
軸(3a) (3a)が定位置で捩れないようlこ補強
せしめている。In this embodiment, as shown in FIG. 1(a), the planetary shaft (3a) (3a) is rotatably attached to the reinforcing plate αO, and the planetary shaft (3a) (3a) is reinforced to prevent it from twisting in place.
このような構成により遊星軸(3a)を外部ケーシング
(2)Iこ弾性支持せしめたため、遊星歯車(3)が太
陽歯車(7)又は内圃車(6)から変動トルクを受けた
場合、遊星軸(3a)に変動トルクが伝わり、前記弾性
支持体(4) (4) (41が円環体(5)を介して
円環状内面突起(ホ)内で圧縮されたり引張られたりし
、加わったトルクに見合って弾性変形する。その作用に
より減速機に加わった変動トルクを吸収する。With this configuration, the planetary shaft (3a) is elastically supported by the outer casing (2), so that when the planetary gear (3) receives fluctuating torque from the sun gear (7) or the inner farm wheel (6), the planetary shaft (3a) A fluctuating torque is transmitted to the shaft (3a), and the elastic support (4) (41) is compressed or pulled within the annular inner protrusion (e) via the torus (5), and the applied force is applied. It deforms elastically in proportion to the applied torque.This action absorbs the fluctuating torque applied to the reducer.
以上説明してきたように本発明の構成によれば、弾性支
持体lこより遊星軸を外部ケーシングlこ弾性支持せし
めており、その弾性変形による振動吸収が著しいため、
スター型遊星歯車装置においても非常に高い変動トルク
吸収効果を得ることができ、又、製造も容易である。As explained above, according to the structure of the present invention, the planetary shaft is elastically supported by the outer casing by the elastic support, and vibration absorption due to the elastic deformation is significant.
Even in a star type planetary gear device, a very high fluctuating torque absorption effect can be obtained, and manufacturing is also easy.
第1図(&) (b)は本発明の一実施例を示す断面図
、第2図はバランスピンを用いた遊星歯車装置内の変動
トルク吸収機構を示す斜視図、第3図はスター型遊星歯
車装置の構造を示す説明図である。
図中、(1)は固定板、(2)は外部ケーシング、(3
)は遊星歯車、(3a)は遊星軸、(4)は弾性支持体
、(5)は円環体、(2)は円環状内面突起、 (so
o)はバランスピンを各示す。
特許出願人 日本鋼管株式袋社
発 明 者 西 川 隆 支間
丸 山 共 −同
服 部 切間
鈴 木 貞 二第 1 図
(”(b)
f42図
第 3 図Fig. 1 (&) (b) is a sectional view showing an embodiment of the present invention, Fig. 2 is a perspective view showing a fluctuating torque absorption mechanism in a planetary gear device using a balance pin, and Fig. 3 is a star type FIG. 2 is an explanatory diagram showing the structure of a planetary gear device. In the figure, (1) is the fixed plate, (2) is the external casing, (3
) is a planetary gear, (3a) is a planetary shaft, (4) is an elastic support, (5) is a torus, (2) is a toroidal inner protrusion, (so
o) shows each balance pin. Patent applicant: Nippon Kokan Kaisha, Ltd. Inventor: Takashi Nishikawa
Joint Maruyama
Kirima Hattori
Teiji Suzuki Figure 1 (''(b) Figure f42 Figure 3
Claims (1)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4840085A JPS61211559A (en) | 1985-03-13 | 1985-03-13 | Star-type planetary gear |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4840085A JPS61211559A (en) | 1985-03-13 | 1985-03-13 | Star-type planetary gear |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS61211559A true JPS61211559A (en) | 1986-09-19 |
Family
ID=12802251
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP4840085A Pending JPS61211559A (en) | 1985-03-13 | 1985-03-13 | Star-type planetary gear |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS61211559A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010151143A (en) * | 2010-03-29 | 2010-07-08 | Hitachi Automotive Systems Ltd | Variable valve operating device for internal combustion engine |
ITTO20111202A1 (en) * | 2011-12-23 | 2013-06-24 | Avio Spa | EPICYCLOIDAL ROTISM |
-
1985
- 1985-03-13 JP JP4840085A patent/JPS61211559A/en active Pending
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010151143A (en) * | 2010-03-29 | 2010-07-08 | Hitachi Automotive Systems Ltd | Variable valve operating device for internal combustion engine |
ITTO20111202A1 (en) * | 2011-12-23 | 2013-06-24 | Avio Spa | EPICYCLOIDAL ROTISM |
EP2607695A1 (en) * | 2011-12-23 | 2013-06-26 | AVIO S.p.A. | Epicyclic gear system |
US8986160B2 (en) | 2011-12-23 | 2015-03-24 | Avio S.P.A. | Epicyclic gear system |
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