JP2007162806A - Multi-stage planetary gear type transmission - Google Patents

Multi-stage planetary gear type transmission Download PDF

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JP2007162806A
JP2007162806A JP2005358884A JP2005358884A JP2007162806A JP 2007162806 A JP2007162806 A JP 2007162806A JP 2005358884 A JP2005358884 A JP 2005358884A JP 2005358884 A JP2005358884 A JP 2005358884A JP 2007162806 A JP2007162806 A JP 2007162806A
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planetary gear
planetary
gear
mechanisms
gear mechanism
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JP4921787B2 (en
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Koichi Kitazawa
浩一 北沢
Masahito Sudo
真仁 須藤
Kyoji Hamamoto
恭司 浜本
Tomohiro Morigami
智博 森上
Isamu Doi
偉 土井
Mikio Kashiwai
幹雄 柏井
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To improve quietness of a multi-stage planetary gear type transmission by reducing noise due to resonance and play. <P>SOLUTION: In the multi-stage planetary gear type transmission with first to third planetary gear mechanisms 50 to 52 connected in series and sharing a ring gear 54, the reduction ratios are made different by differentiating the gear number ratios of sun gears 53, 57, 60 of the first to third planetary gear mechanisms 50 to 52 and planetary gears 55, 58, 62, so that the vibration frequency and phase generated from each of the planetary gear mechanisms 50 to 52 are made different and the noise due to resonance can be reduced. Further, because the phase of backlash of engaging parts of each of the planetary gear mechanisms 50 to 52 can be made different, in the case there is an input in both normal and reverse directions from a rotary shaft 46 of a motor M to the first planetary gear mechanism 50, the occurrence of play is suppressed and the noise can be reduced. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、各々がサンギヤ、リングギヤ、プラネタリギヤおよびプラネタリキャリヤを備えた複数の遊星歯車機構を直列に接続し、各遊星歯車機構のリングギヤを共有化した多段遊星歯車式変速機に関する。   The present invention relates to a multi-stage planetary gear type transmission in which a plurality of planetary gear mechanisms each including a sun gear, a ring gear, a planetary gear, and a planetary carrier are connected in series, and the ring gears of the planetary gear mechanisms are shared.

各々がサンギヤ、リングギヤ、プラネタリギヤおよびプラネタリキャリヤを備えた３個の遊星歯車機構を直列に配置し、１段目の遊星歯車機構のプラネタリキャリヤを２段目の遊星歯車機構のサンギヤに接続し、２段目の遊星歯車機構のプラネタリキャリヤを３段目の遊星歯車機構のサンギヤに接続し、１段目の遊星歯車機構のサンギヤに入力される回転を３段目の遊星歯車機構のプラネタリキャリヤに減速して出力させる変速装置が、下記特許文献１により公知である。
実開平５−３１８７４号公報 Three planetary gear mechanisms each including a sun gear, a ring gear, a planetary gear and a planetary carrier are arranged in series, and the planetary carrier of the first stage planetary gear mechanism is connected to the sun gear of the second stage planetary gear mechanism. The planetary carrier of the stage planetary gear mechanism is connected to the sun gear of the planetary gear mechanism of the third stage, and the rotation input to the sun gear of the planetary gear mechanism of the first stage is reduced to the planetary carrier of the planetary gear mechanism of the third stage. Japanese Patent Application Laid-Open Publication No. 2004-228561 discloses a transmission device that outputs the output.
Japanese Utility Model Publication No. 5-31874

ところで上記従来のものは、部品の種類および個数を削減するために、サンギヤ、リングギヤおよびプラネタリギヤの歯数が１段目〜３段目の遊星歯車機構で同一に設定されており、かつ１個のリングギヤが３個の遊星歯車機構に対して共有されているので、３個の遊星歯車機構から周波数および位相が同一の振動が発生し、その共振により騒音が増加するという問題があった。また入力軸を小さい周期で正逆回転させる場合には、３個の遊星歯車機構のギヤの噛合部のバックラッシュの位相が同一になるため、ガタが発生して騒音が増加する問題があった。   By the way, in the above conventional one, in order to reduce the types and the number of parts, the number of teeth of the sun gear, the ring gear and the planetary gear is set to be the same in the first to third stage planetary gear mechanisms, and one Since the ring gear is shared by the three planetary gear mechanisms, there is a problem that vibrations having the same frequency and phase are generated from the three planetary gear mechanisms, and noise increases due to the resonance. In addition, when the input shaft is rotated forward and backward with a small period, the backlash phases of the meshing portions of the three planetary gear mechanisms are the same, and thus there is a problem that rattling occurs and noise increases. .

本発明は前述の事情に鑑みてなされたもので、多段遊星歯車式変速機の静粛性を改善することを目的とする。   The present invention has been made in view of the above circumstances, and an object thereof is to improve the quietness of a multi-stage planetary gear type transmission.

上記目的を達成するために、請求項１に記載された発明によれば、各々がサンギヤ、リングギヤ、プラネタリギヤおよびプラネタリキャリヤを備えた複数の遊星歯車機構を直列に接続し、各遊星歯車機構のリングギヤを共有化した多段遊星歯車式変速機において、前記複数の遊星歯車機構の変速比を異ならせたことを特徴とする多段遊星歯車式変速機が提案される。   To achieve the above object, according to the first aspect of the present invention, a plurality of planetary gear mechanisms each including a sun gear, a ring gear, a planetary gear and a planetary carrier are connected in series, and the ring gear of each planetary gear mechanism is connected. A multi-stage planetary gear type transmission in which the gear ratios of the plurality of planetary gear mechanisms are made different is proposed.

尚、実施例の第１遊星歯車機構５０、第２遊星歯車機構５１および第３遊星歯車機構５２は本発明の遊星歯車機構に対応する。   Note that the first planetary gear mechanism 50, the second planetary gear mechanism 51, and the third planetary gear mechanism 52 of the embodiment correspond to the planetary gear mechanism of the present invention.

請求項１の構成によれば、複数の遊星歯車機構を直列に接続してリングギヤを共有化した多段遊星歯車式変速機において、複数の遊星歯車機構の変速比を異ならせたので、各遊星歯車機構から発生する振動の周波数および位相を異ならせて共振による騒音を低減するとともに、正逆両方向の入力がある場合に各遊星歯車機構のギヤの噛合部のバックラッシュの位相を異ならせ、ガタの増加を抑制して騒音を低減することができる。   According to the configuration of claim 1, in the multi-stage planetary gear type transmission in which a plurality of planetary gear mechanisms are connected in series to share a ring gear, the speed ratios of the plurality of planetary gear mechanisms are different. The frequency and phase of vibration generated from the mechanism are varied to reduce noise due to resonance, and when there is an input in both forward and reverse directions, the backlash phase of the gear meshing portion of each planetary gear mechanism is differentiated. The increase can be suppressed and noise can be reduced.

以下、本発明の実施の形態を、添付の図面に示した本発明の実施例に基づいて説明する。   DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on examples of the present invention shown in the accompanying drawings.

図１および図２は本発明の一実施例を示すもので、図１はアクティブサスペンション装置の斜視図、図２は図１の２−２線拡大断面図である。   1 and 2 show an embodiment of the present invention. FIG. 1 is a perspective view of an active suspension device, and FIG. 2 is an enlarged sectional view taken along line 2-2 of FIG.

図１に示すように、車輪Ｗを回転自在に支持するナックル１１を車体に懸架するマルチリンク式のサスペンション装置Ｓは、車幅方向に延びるロアーム１２と、車幅方向に延びるアッパーアーム１３と、車体から斜め前方に延びるトレーリングアーム１４と、車体から斜め後方に延びるリーディングアーム１５と、車幅方向に延びるラテラルアーム１６とを介して上下動自在に支持される。車輪Ｗの上下動を緩衝するダンパー１７の下端がナックル１１に接続されるとともに、左右の車輪Ｗ，Ｗの上下動を相互に連動させて車体のローリングを抑制するスタビライザー１８の車幅方向外端がリンク１９を介してナックル１１に接続される。そして車体にブラケット２０を介して支持した電動アクチュエータＡにより揺動する駆動アーム２１の先端が、ロアアーム１２の中間部にリンク２２を介して接続される。   As shown in FIG. 1, a multi-link suspension device S that suspends a knuckle 11 that rotatably supports a wheel W on a vehicle body includes a lower arm 12 that extends in the vehicle width direction, an upper arm 13 that extends in the vehicle width direction, It is supported by a trailing arm 14 extending obliquely forward from the vehicle body, a leading arm 15 extending obliquely rearward from the vehicle body, and a lateral arm 16 extending in the vehicle width direction so as to be movable up and down. The lower end of the damper 17 that buffers the vertical movement of the wheel W is connected to the knuckle 11 and the vertical end of the stabilizer 18 that suppresses rolling of the vehicle body by interlocking the vertical movement of the left and right wheels W and W with each other. Is connected to the knuckle 11 via the link 19. Then, the tip of the drive arm 21 that swings by the electric actuator A supported by the vehicle body via the bracket 20 is connected to the intermediate portion of the lower arm 12 via the link 22.

図２に示すように、電動アクチュエータＡはモータＭと減速機Ｇとで構成されており、減速機Ｇのハウジングは第１減速機ハウジング４１および第２減速機ハウジング４２のフランジ４１ａ，４２ａどうしをボルト４３…で結合してなり、モータハウジング４４はボルト４５…で第２減速機ハウジング４２に結合される。第１、第２減速機ハウジング４１，４２の内部に突出するモータＭの回転軸４６と、第１減速機ハウジング４１に一対のボールベアリング４７，４８で支持された出力軸４９とが軸線Ｌ上に配置されており、モータＭの回転軸４６の回転が第１遊星歯車機構５０、第２遊星歯車機構５１および第３遊星歯車機構５２を介して出力軸４９に伝達される。   As shown in FIG. 2, the electric actuator A is composed of a motor M and a reduction gear G, and the housing of the reduction gear G includes flanges 41 a and 42 a of the first reduction gear housing 41 and the second reduction gear housing 42. The motor housing 44 is coupled to the second reduction gear housing 42 by bolts 45... A rotation shaft 46 of the motor M protruding inside the first and second reduction gear housings 41 and 42 and an output shaft 49 supported on the first reduction gear housing 41 by a pair of ball bearings 47 and 48 are on the axis L. The rotation of the rotating shaft 46 of the motor M is transmitted to the output shaft 49 via the first planetary gear mechanism 50, the second planetary gear mechanism 51, and the third planetary gear mechanism 52.

第１遊星歯車機構５０は、モータＭの回転軸４６に固定されたサンギヤ５３と、第１減速機ハウジング４１の内面に固定されたリングギヤ５４と、サンギヤ５３およびリングギヤ５４に同時に噛合する複数のプラネタリギヤ５５…と、プラネタリギヤ５５…を回転自在に支持するプラネタリキャリア５６とで構成される。   The first planetary gear mechanism 50 includes a sun gear 53 fixed to the rotation shaft 46 of the motor M, a ring gear 54 fixed to the inner surface of the first reduction gear housing 41, and a plurality of planetary gears that simultaneously mesh with the sun gear 53 and the ring gear 54. And planetary carriers 56 that rotatably support the planetary gears 55.

第２遊星歯車機構５１は、第１遊星歯車機構５０のプラネタリキャリア５６に固定されたサンギヤ５７と、第１遊星歯車機構５０に共用されるリングギヤ５４と、サンギヤ５７およびリングギヤ５４に同時に噛合する複数のプラネタリギヤ５８…と、プラネタリギヤ５８…を回転自在に支持するプラネタリキャリア５９とで構成される。   The second planetary gear mechanism 51 includes a sun gear 57 fixed to the planetary carrier 56 of the first planetary gear mechanism 50, a ring gear 54 shared by the first planetary gear mechanism 50, and a plurality of gears simultaneously meshed with the sun gear 57 and the ring gear 54. Planetary gears 58 and a planetary carrier 59 that rotatably supports the planetary gears 58.

第３遊星歯車機構５２は、第２遊星歯車機構５１のプラネタリキャリア５９に固定されたサンギヤ６０と、第１、第２遊星歯車機構５０，５１に共用されるリングギヤ５４と、サンギヤ６０およびリングギヤ５４に同時に噛合する複数のプラネタリギヤ６２…と、プラネタリギヤ６２…を回転自在に支持するプラネタリキャリア６３とで構成されており、このプラネタリキャリア６３に出力軸４９が固定される。   The third planetary gear mechanism 52 includes a sun gear 60 fixed to the planetary carrier 59 of the second planetary gear mechanism 51, a ring gear 54 shared by the first and second planetary gear mechanisms 50 and 51, and the sun gear 60 and the ring gear 54. And a planetary carrier 63 that rotatably supports the planetary gears 62. An output shaft 49 is fixed to the planetary carrier 63.

第１〜第３遊星歯車機構５０〜５２の３個のサンギヤ５３，５７，６０のうち、第１遊星歯車機構５０のサンギヤ５３の歯数が最も小さく、第２遊星歯車機構５１のサンギヤ５７の歯数が最も大きく、第３遊星歯車機構５２のサンギヤ６０の歯数が両者の中間の大きさに設定される。これに伴い、第１〜第３遊星歯車機構５０〜５２の３種のプラネタリギヤ５５…，５８…，６２…のうち、第１遊星歯車機構５０のプラネタリギヤ５５…の歯数が最も大きく、第２遊星歯車機構５１のプラネタリギヤ５８…の歯数が最も小さく、第３遊星歯車機構５２のプラネタリギヤ６２…の歯数が両者の中間の大きさに設定される。尚、部品点数を減少させるべく、第１〜第３遊星歯車機構５０〜５２のリングギヤ５４は共用されているため、その歯数は当然同じである。   Of the three sun gears 53, 57, 60 of the first to third planetary gear mechanisms 50 to 52, the sun gear 53 of the first planetary gear mechanism 50 has the smallest number of teeth, and the sun gear 57 of the second planetary gear mechanism 51 has The number of teeth is the largest, and the number of teeth of the sun gear 60 of the third planetary gear mechanism 52 is set to an intermediate size. Accordingly, the planetary gear 55 of the first planetary gear mechanism 50 has the largest number of teeth among the three types of planetary gears 55, 58, 62, of the first to third planetary gear mechanisms 50 to 52, and the second The number of teeth of the planetary gears 58 of the planetary gear mechanism 51 is the smallest, and the number of teeth of the planetary gears 62 of the third planetary gear mechanism 52 is set to an intermediate size between them. In addition, since the ring gear 54 of the 1st-3rd planetary gear mechanisms 50-52 is shared in order to reduce a number of parts, the number of teeth is naturally the same.

これにより、例えば第１遊星歯車機構５０の減速比は５．５に、第２遊星歯車機構５１の減速比は４．０に、第３遊星歯車機構５２の減速比は５．０に設定される。   Thereby, for example, the reduction ratio of the first planetary gear mechanism 50 is set to 5.5, the reduction ratio of the second planetary gear mechanism 51 is set to 4.0, and the reduction ratio of the third planetary gear mechanism 52 is set to 5.0. The

しかして、第１減速機ハウジング４１の取付部４１ｂが、車体に固定された前記ブラケット２０にボルト６４およびナット６５で締結される。   Accordingly, the mounting portion 41 b of the first reduction gear housing 41 is fastened to the bracket 20 fixed to the vehicle body with the bolt 64 and the nut 65.

次に、上記構成を備えた本発明の実施例の作用について説明する。   Next, the operation of the embodiment of the present invention having the above configuration will be described.

電動アクチュエータＡのモータＭを駆動すると、モータＭの回転軸４６に固定した第１遊星歯車機構５０のサンギヤ５３が回転し、このサンギヤ５３およびリングギヤ５４に噛合するプラネタリギヤ５５…が自転しながらプラネタリキャリア５６を公転させる。プラネタリキャリア５６に固定した第２遊星歯車機構５１のサンギヤ５７が回転すると、このサンギヤ５７およびリングギヤ５４に噛合するプラネタリギヤ５８…が自転しながらプラネタリキャリア５９を公転させる。プラネタリキャリア５９に固定した第３遊星歯車機構５２のサンギヤ６０が回転すると、このサンギヤ６０およびリングギヤ５４に噛合するプラネタリギヤ６２…が自転しながらプラネタリキャリア６３を公転させるので、プラネタリキャリア６３に固定した出力軸４９が軸線Ｌまわりに回転する。   When the motor M of the electric actuator A is driven, the sun gear 53 of the first planetary gear mechanism 50 fixed to the rotary shaft 46 of the motor M rotates, and the planetary gear 55 meshing with the sun gear 53 and the ring gear 54 rotates while the planetary carrier rotates. Revolve 56. When the sun gear 57 of the second planetary gear mechanism 51 fixed to the planetary carrier 56 rotates, the planetary gears 58 meshing with the sun gear 57 and the ring gear 54 revolve the planetary carrier 59 while rotating. When the sun gear 60 of the third planetary gear mechanism 52 fixed to the planetary carrier 59 rotates, the planetary gears 62 meshing with the sun gear 60 and the ring gear 54 revolve the planetary carrier 63 while rotating, so the output fixed to the planetary carrier 63 The shaft 49 rotates around the axis L.

このように、モータＭの回転軸４６と出力軸４９との間に第１〜第３遊星歯車機構５０〜５２を直列に配置したので、モータＭの回転数を大きな減速比で減速して駆動アーム２１を大きなトルクで駆動することができる。モータＭのトルクは第１〜第３遊星歯車機構５０〜５２により次第に増加するため、第１遊星歯車機構５０の各ギヤの歯厚、第２遊星歯車機構５１の各ギヤの歯厚、第３遊星歯車機構５２の各ギヤの歯厚は次第に厚くなっている。   As described above, since the first to third planetary gear mechanisms 50 to 52 are arranged in series between the rotating shaft 46 and the output shaft 49 of the motor M, the motor M is driven at a reduced speed with a large reduction ratio. The arm 21 can be driven with a large torque. Since the torque of the motor M is gradually increased by the first to third planetary gear mechanisms 50 to 52, the tooth thickness of each gear of the first planetary gear mechanism 50, the tooth thickness of each gear of the second planetary gear mechanism 51, the third The gear thickness of each gear of the planetary gear mechanism 52 is gradually increased.

上述のようにして駆動アーム２１が揺動すると、この駆動アーム２１にリンク２２を介して接続されたロアーム１２が上下動することで、車体に対するナックル１１の位置、つまり車輪Ｗの位置を積極的に変化させ、これにより乗り心地性能や操縦安定性能を向上させることができる。   When the drive arm 21 swings as described above, the lower arm 12 connected to the drive arm 21 via the link 22 moves up and down, so that the position of the knuckle 11 relative to the vehicle body, that is, the position of the wheel W is positive. This makes it possible to improve riding comfort performance and steering stability performance.

さて、第１遊星歯車機構５０のサンギヤ５３およびプラネタリギヤ５５の歯数と、第２遊星歯車機構５１のサンギヤ５７およびプラネタリギヤ５８の歯数と、第３遊星歯車機構５２のサンギヤ６０およびプラネタリギヤ６２の歯数とが同一であると仮定すると、第１〜第３遊星歯車機構５０〜５２が一つのリングギヤ５４を共用していることから、第１〜第３遊星歯車機構５０〜５２から周波数および位相が同一の振動が発生してしまい、その共振により騒音が増加する可能性がある。またモータＭの回転軸４６が小さい周期で正逆回転すると、第１〜第３遊星歯車機構５０〜５２のギヤの噛合部のバックラッシュの位相も同一になるため、ガタが発生して騒音が増加する可能性がある。   Now, the number of teeth of the sun gear 53 and the planetary gear 55 of the first planetary gear mechanism 50, the number of teeth of the sun gear 57 and the planetary gear 58 of the second planetary gear mechanism 51, and the teeth of the sun gear 60 and the planetary gear 62 of the third planetary gear mechanism 52. Assuming that the numbers are the same, since the first to third planetary gear mechanisms 50 to 52 share one ring gear 54, the frequency and phase are changed from the first to third planetary gear mechanisms 50 to 52. The same vibration is generated, and the noise may increase due to the resonance. Further, when the rotation shaft 46 of the motor M rotates forward and backward with a small cycle, the backlash phase of the meshing portion of the gears of the first to third planetary gear mechanisms 50 to 52 becomes the same, so that play occurs and noise is generated. May increase.

しかしながら、本実施例によれば、第１〜第３遊星歯車機構５０〜５２の減速比をそれぞれ異ならせたので、第１〜第３遊星歯車機構５０〜５２から発生する振動の周波数および位相を異ならせて共振による騒音を低減することができるだけなく、第１〜第３遊星歯車機構５０〜５２のギヤの噛合部のバックラッシュの位相を異ならせることで、モータＭの回転軸４６が小さい周期で正逆回転する場合にガタの発生を抑制して騒音を低減することができる。   However, according to the present embodiment, since the reduction ratios of the first to third planetary gear mechanisms 50 to 52 are made different from each other, the frequency and phase of vibration generated from the first to third planetary gear mechanisms 50 to 52 are changed. It is possible not only to reduce noise due to resonance, but also to change the backlash phase of the meshing portion of the gears of the first to third planetary gear mechanisms 50 to 52 so that the rotation shaft 46 of the motor M has a small cycle. In the case of forward and reverse rotation, it is possible to suppress the generation of backlash and reduce noise.

以上、本発明の実施例を説明したが、本発明はその要旨を逸脱しない範囲で種々の設計変更を行うことが可能である。   Although the embodiments of the present invention have been described above, various design changes can be made without departing from the scope of the present invention.

例えば、本発明の多段遊星歯車式変速機は、実施例のマルチリンク式のサスペンション装置Ｓ以外の任意の用途に適用することができる。   For example, the multi-stage planetary gear type transmission of the present invention can be applied to any application other than the multi-link type suspension device S of the embodiment.

また遊星歯車機構のプラネタリキャリヤを入力要素としてサンギヤを出力要素とすると増速機になるため、本発明の多段遊星歯車式変速機は増速機に対しても適用することができる。   Further, since the planetary carrier of the planetary gear mechanism is used as an input element and the sun gear is used as an output element, it becomes a speed increaser. Therefore, the multistage planetary gear type transmission of the present invention can also be applied to a speed increaser.

また実施例では３個の遊星歯車機構を直列に接続しているが、２個あるいは４個以上の遊星歯車機構を直列に接続しても良い。   In the embodiment, three planetary gear mechanisms are connected in series, but two or four or more planetary gear mechanisms may be connected in series.

アクティブサスペンション装置の斜視図Perspective view of active suspension device 図１の２−２線拡大断面図2-2 line enlarged sectional view of FIG.

符号の説明Explanation of symbols

５０ 第１遊星歯車機構（遊星歯車機構）
５１ 第２遊星歯車機構（遊星歯車機構）
５２ 第３遊星歯車機構（遊星歯車機構）
５３ サンギヤ
５４ リングギヤ
５５ プラネタリギヤ
５６ プラネタリキャリヤ
５７ サンギヤ
５８ プラネタリギヤ
５９ プラネタリキャリヤ
６０ サンギヤ
６２ プラネタリギヤ
６３ プラネタリキャリヤ
50 First planetary gear mechanism (planetary gear mechanism)
51 Second planetary gear mechanism (planetary gear mechanism)
52 3rd planetary gear mechanism (planetary gear mechanism)
53 Sun gear 54 Ring gear 55 Planetary gear 56 Planetary carrier 57 Sun gear 58 Planetary gear 59 Planetary carrier 60 Sun gear 62 Planetary gear 63 Planetary carrier

Claims (1)

各々がサンギヤ（５３，５７，６０）、リングギヤ（５４）、プラネタリギヤ（５５，５８，６２）およびプラネタリキャリヤ（５６，５９，６３）を備えた複数の遊星歯車機構（５０，５１，５２）を直列に接続し、各遊星歯車機構（５０，５１，５２）のリングギヤ（５４）を共有化した多段遊星歯車式変速機において、
前記複数の遊星歯車機構（５０，５１，５２）の変速比を異ならせたことを特徴とする多段遊星歯車式変速機。
A plurality of planetary gear mechanisms (50, 51, 52) each including a sun gear (53, 57, 60), a ring gear (54), a planetary gear (55, 58, 62) and a planetary carrier (56, 59, 63). In a multi-stage planetary gear type transmission connected in series and sharing the ring gear (54) of each planetary gear mechanism (50, 51, 52),
A multi-stage planetary gear type transmission, wherein the plurality of planetary gear mechanisms (50, 51, 52) have different gear ratios.
JP2005358884A 2005-12-13 2005-12-13 Multi-stage planetary gear type transmission Expired - Fee Related JP4921787B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010216590A (en) * 2009-03-17 2010-09-30 Jtekt Corp Rocking type gear device
WO2019074118A1 (en) * 2017-10-13 2019-04-18 アイシン・エィ・ダブリュ株式会社 Drive device for vehicle

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6435237A (en) * 1987-07-30 1989-02-06 Anritsu Corp Abnormality diagnosis for rotary machine
JPH04131541A (en) * 1990-09-25 1992-05-06 Hitachi Constr Mach Co Ltd Planetary gear speed reducer
JPH10159914A (en) * 1996-11-25 1998-06-16 Hitachi Constr Mach Co Ltd Planetary gear reduction gear
JPH10311384A (en) * 1997-05-09 1998-11-24 Namiki Precision Jewel Co Ltd Epicycle reduction gear and assembly method therefor
JPH1137225A (en) * 1997-07-16 1999-02-12 Nabco Ltd Reduction gear

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6435237A (en) * 1987-07-30 1989-02-06 Anritsu Corp Abnormality diagnosis for rotary machine
JPH04131541A (en) * 1990-09-25 1992-05-06 Hitachi Constr Mach Co Ltd Planetary gear speed reducer
JPH10159914A (en) * 1996-11-25 1998-06-16 Hitachi Constr Mach Co Ltd Planetary gear reduction gear
JPH10311384A (en) * 1997-05-09 1998-11-24 Namiki Precision Jewel Co Ltd Epicycle reduction gear and assembly method therefor
JPH1137225A (en) * 1997-07-16 1999-02-12 Nabco Ltd Reduction gear

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010216590A (en) * 2009-03-17 2010-09-30 Jtekt Corp Rocking type gear device
WO2019074118A1 (en) * 2017-10-13 2019-04-18 アイシン・エィ・ダブリュ株式会社 Drive device for vehicle
CN111133225A (en) * 2017-10-13 2020-05-08 爱信艾达株式会社 Vehicle drive device
JPWO2019074118A1 (en) * 2017-10-13 2020-08-27 アイシン・エィ・ダブリュ株式会社 Vehicle drive
US11015683B2 (en) 2017-10-13 2021-05-25 Aisin Aw Co., Ltd. Vehicle driving device

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