JP2016109146A - Two-stage transmission - Google Patents

Two-stage transmission Download PDF

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JP2016109146A
JP2016109146A JP2014243894A JP2014243894A JP2016109146A JP 2016109146 A JP2016109146 A JP 2016109146A JP 2014243894 A JP2014243894 A JP 2014243894A JP 2014243894 A JP2014243894 A JP 2014243894A JP 2016109146 A JP2016109146 A JP 2016109146A
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carrier
planetary gear
input shaft
output
shaft
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JP6517502B2 (en
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研吾 小林
Kengo Kobayashi
研吾 小林
年昭 的場
Toshiaki Matoba
年昭 的場
寿夫 越野
Toshio Koshino
寿夫 越野
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MATEX KK
IHI Aerospace Co Ltd
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MATEX KK
IHI Aerospace Co Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a two-stage transmission capable of realizing simplification of a structure in addition to reduction of a size and a weight.SOLUTION: A two-stage transmission includes a planetary gear mechanism 10 including an input shaft 2 to which rotation output is given, an output shaft 3, a sun gear 11 formed on the input shaft 2, an annular gear 12 disposed around the sun gear 11, a planetary gear 13 engaged with both of the sun gear 11 and the annular gear 12, and a carrier 14 lowering the rotation output given to the input shaft 2 by rotatably supporting the planetary gear 13 fixed to the output shaft 3, and outputting the same. A clutch mechanism 20 is disposed to switch a low-speed mode for keeping the annular gear 12 of the planetary gear mechanism 10 in a fixed state, lowering the rotation output given to the input shaft 2 by the planetary gear mechanism 10, and outputting the same to the output shaft 3, and a high-speed mode for outputting the rotation output given to the input shaft 2 to the output shaft 3 as it is through the carrier 14 of the planetary gear mechanism 10.SELECTED DRAWING: Figure 2

Description

本発明は、例えば、電気自動車に搭載されて、モータから入力する回転力を高速モード及び低速モードの二段階に切り換えて出力する二段変速機に関するものである。   The present invention relates to a two-stage transmission that is mounted on, for example, an electric vehicle and outputs a rotational force input from a motor by switching between two stages of a high speed mode and a low speed mode.

従来、上記したような二段変速機としては、例えば、特許文献１に記載されたものがあり、この二段変速機は、モータに連結される入力軸と、出力軸と、入力軸及び出力軸の双方に連結する遊星歯車機構を備えている。   Conventionally, as the above-described two-stage transmission, for example, there is one described in Patent Document 1, and this two-stage transmission includes an input shaft connected to a motor, an output shaft, an input shaft, and an output. A planetary gear mechanism connected to both of the shafts is provided.

この遊星歯車機構は、入力軸に固定される太陽歯車と、この太陽歯車の周囲に配置される環状歯車と、太陽歯車及び環状歯車の双方に噛み合う遊星歯車と、この遊星歯車を回転自在に支持することで入力軸に付与されたモータからの回転出力を落として出力するキャリアを具備している。   The planetary gear mechanism includes a sun gear fixed to the input shaft, an annular gear arranged around the sun gear, a planetary gear meshing with both the sun gear and the annular gear, and the planetary gear rotatably supported. By doing so, a carrier is provided that outputs the rotational output from the motor applied to the input shaft.

また、この二段変速機では、遊星歯車機構の環状歯車を固定状態としたうえで、この環状歯車に対して回転するキャリア及び入力軸のいずれかを選択して出力軸に接続するクラッチ機構を備えている。   Further, in this two-stage transmission, a clutch mechanism that selects a carrier rotating with respect to the annular gear and an input shaft and connects it to the output shaft after the annular gear of the planetary gear mechanism is fixed. I have.

このクラッチ機構は、環状歯車に対して回転するキャリアに形成されて入力軸に嵌装する筒部と、このキャリアの筒部の内側で入力軸に回転自在で且つ軸方向に移動可能に嵌装されると共に、端部が出力軸に軸方向に移動可能で且つ回転不能に嵌合されたスリーブと、スリーブの入力軸に嵌装する部分に保持されたトルク伝達用ボールと、キャリアの筒部及び入力軸に互いに軸方向にずらせてそれぞれ形成されて、スリーブのトルク伝達用ボールと係合して各々の回転をスリーブに伝達する係合部と、スリーブに保持されたトルク伝達用ボールがキャリアの係合部と係合する位置と入力軸の係合部と係合する位置との間で該スリーブを移動させる駆動部を具備している。   This clutch mechanism is formed on a carrier that is formed on a carrier that rotates with respect to an annular gear and is fitted to an input shaft, and is fitted inside the cylinder of the carrier so as to be rotatable on the input shaft and movable in the axial direction. A sleeve that is axially movable and non-rotatably fitted to the output shaft, a torque transmitting ball held on a portion of the sleeve fitted to the input shaft, and a carrier cylinder And an input shaft that is formed to be axially shifted from each other, engages with a torque transmission ball of the sleeve and transmits each rotation to the sleeve, and a torque transmission ball held by the sleeve is a carrier. And a drive section for moving the sleeve between a position where it engages with the engaging section and a position where it engages with the engaging section of the input shaft.

この二段変速機において、クラッチ機構の駆動部によりスリーブを軸方向に移動させて、このスリーブに保持されたトルク伝達用ボールを入力軸の係合部に係合させることで、入力軸に付与されたモータからの回転出力をそのまま出力軸に伝達し、一方、クラッチ機構の駆動部によりスリーブを軸方向に移動させて、このスリーブに保持されたトルク伝達用ボールを環状歯車に対して回転するキャリアの係合部に係合させることで、遊星歯車機構を作動させて、モータからの回転出力を低速にして出力軸に伝達するようになっている。   In this two-stage transmission, the sleeve is moved in the axial direction by the driving portion of the clutch mechanism, and the torque transmission ball held by the sleeve is engaged with the engaging portion of the input shaft, thereby being applied to the input shaft. The rotation output from the motor is transmitted to the output shaft as it is, while the sleeve is moved in the axial direction by the driving portion of the clutch mechanism, and the torque transmission ball held by the sleeve is rotated with respect to the annular gear. By engaging with the engaging portion of the carrier, the planetary gear mechanism is operated, and the rotational output from the motor is reduced in speed and transmitted to the output shaft.

このように、この二段変速機では、減速されていない高速回転出力と、減速された低速回転出力とを一つのクラッチ機構によって選択的に切り換えて出力軸に出力するようにしているので、重量の嵩む摩擦クラッチを複数組必要としない分だけ、小型軽量化が図られることとなる。   Thus, in this two-stage transmission, the high-speed rotation output that is not decelerated and the low-speed rotation output that is decelerated are selectively switched by one clutch mechanism and output to the output shaft. Therefore, the size and weight can be reduced by the amount that does not require a plurality of friction clutches.

特開2011-220484号公報JP 2011-220484 A

ところが、上記した従来の二段変速機において、減速されていない高速回転出力及び減速された低速回転出力のいずれかを選択して出力軸に伝達するのに、重量の嵩む摩擦クラッチを使用していないので、その分だけ小型軽量化を実現することができるものの、クラッチ機構の構造として、スリーブに保持されたトルク伝達用ボールがキャリアの係合部と係合する位置と入力軸の係合部と係合する位置との間でスリーブを軸方向に移動させる構造を採用しているので、クラッチ機構の構造が簡略であるとは言い難いという問題があり、この問題を解決することが従来の課題となっていた。   However, in the conventional two-stage transmission described above, a heavy friction clutch is used to select and transmit either the undecelerated high-speed rotation output or the decelerated low-speed rotation output to the output shaft. Therefore, although the size and weight can be reduced by that much, the clutch mechanism is structured so that the torque transmission ball held by the sleeve engages with the carrier engaging portion and the input shaft engaging portion. Since the structure in which the sleeve is moved in the axial direction between the engagement position and the engagement position is employed, it is difficult to say that the structure of the clutch mechanism is simple. It was an issue.

本発明は、上記した従来の課題に着目してなされたもので、小型軽量化に加えて構造の簡略化をも実現することが可能である二段変速機を提供することを目的としている。   The present invention has been made paying attention to the above-described conventional problems, and an object thereof is to provide a two-stage transmission capable of realizing a simplified structure in addition to a reduction in size and weight.

本発明の第１の態様は、入力軸と、出力軸と、前記入力軸と同軸回転する太陽歯車と、この太陽歯車を囲んで配置される環状歯車と、前記太陽歯車及び環状歯車の双方に噛み合う遊星歯車と、前記出力軸に固定されて前記遊星歯車を回転自在に支持することで前記入力軸に付与される回転出力を落として出力するキャリアを具備した遊星歯車機構を備え、前記遊星歯車機構の環状歯車を固定状態とし、前記入力軸に付与される回転出力を前記遊星歯車機構で落として前記出力軸に出力する低速モードと、前記入力軸に付与される回転出力を前記遊星歯車機構の前記キャリアを介して前記出力軸にそのまま出力する高速モードとを切り換えるクラッチ機構を設けた構成としている。   A first aspect of the present invention includes an input shaft, an output shaft, a sun gear that rotates coaxially with the input shaft, an annular gear disposed around the sun gear, and both the sun gear and the annular gear. A planetary gear mechanism having a meshing planetary gear and a carrier fixed to the output shaft and rotatably supporting the planetary gear to reduce the rotational output applied to the input shaft and outputting the planetary gear. A low-speed mode in which an annular gear of the mechanism is fixed, a rotation output applied to the input shaft is dropped by the planetary gear mechanism and output to the output shaft, and a rotation output applied to the input shaft is output to the planetary gear mechanism A clutch mechanism for switching between a high-speed mode in which the output is output to the output shaft as it is via the carrier is provided.

また、本発明の第２の態様において、前記クラッチ機構は、前記入力軸に軸方向に移動可能で且つ回転不能に嵌合されたスライド筒と、前記入力軸に嵌合された前記スライド筒に配置された筒側係合部と、前記遊星歯車機構の前記遊星歯車を回転自在に支持する前記キャリアに配置されて、前記スライド筒の前記筒側係合部と互いに係合することで前記入力軸の回転が該キャリアにそのまま伝達されるキャリア側係合部と、前記低速モードにおける前記スライド筒の前記筒側係合部が前記キャリアの前記キャリア側係合部から離れた位置、及び、前記高速モードにおける前記スライド筒の前記筒側係合部が前記キャリアの前記キャリア側係合部と係合する位置の間で該スライド筒を移動させる駆動部を具備している構成としている。   In the second aspect of the present invention, the clutch mechanism may include a slide cylinder that is axially movable and non-rotatably fitted to the input shaft, and a slide cylinder that is fitted to the input shaft. The cylinder-side engaging portion that is arranged and the carrier that rotatably supports the planetary gear of the planetary gear mechanism are arranged to engage with the cylinder-side engaging portion of the slide cylinder to engage the input. A carrier-side engaging portion in which rotation of the shaft is transmitted to the carrier as it is, a position where the cylinder-side engaging portion of the slide cylinder in the low-speed mode is separated from the carrier-side engaging portion of the carrier, and In the high-speed mode, a drive unit is provided that moves the slide cylinder between positions where the cylinder-side engagement part of the slide cylinder engages with the carrier-side engagement part of the carrier.

さらに、本発明の第３の態様において、前記キャリアの前記キャリア側係合部は、前記キャリアに固定されて前記遊星歯車機構の前記遊星歯車を回転自在に支持する歯車軸の先端部である構成としている。   Furthermore, in the third aspect of the present invention, the carrier-side engaging portion of the carrier is a tip portion of a gear shaft that is fixed to the carrier and rotatably supports the planetary gear of the planetary gear mechanism. It is said.

本発明の請求項１に係る二段変速機では、クラッチ機構によって高速モードを選択すると、入力軸に付与された回転出力が高速のまま遊星歯車機構のキャリアを介して出力軸に伝達され、一方、クラッチ機構によって低速モードに切り換えると、入力軸に付与される回転出力が遊星歯車機構で落とされて出力軸に伝達されることとなる。   In the two-stage transmission according to the first aspect of the present invention, when the high speed mode is selected by the clutch mechanism, the rotational output applied to the input shaft is transmitted to the output shaft through the carrier of the planetary gear mechanism at a high speed, When the low speed mode is switched by the clutch mechanism, the rotational output applied to the input shaft is dropped by the planetary gear mechanism and transmitted to the output shaft.

このように、減速されていない高速回転出力と、減速された低速回転出力とを一つのクラッチ機構によって選択的に切り換えて出力軸に出力するようにしているので、重量の嵩む摩擦クラッチを複数組必要としない分だけ、小型軽量化が図られることとなる。   In this way, the high-speed rotation output that has not been decelerated and the low-speed rotation output that has been decelerated are selectively switched by a single clutch mechanism and output to the output shaft. The size and weight can be reduced by the amount not required.

特に、高速モードでは、入力軸に付与された回転出力を遊星歯車機構のキャリアを介してそのまま出力軸に伝達するようにしているので、構造の簡略化も図られることとなる。   In particular, in the high-speed mode, the rotational output applied to the input shaft is directly transmitted to the output shaft via the carrier of the planetary gear mechanism, so that the structure can be simplified.

加えて、遊星歯車機構の環状歯車を固定状態としている、すなわち、遊星歯車機構を構成する歯車群のうちの環状歯車を固定状態としているので、環状歯車が回転しない分だけ、高速回転出力時における慣性負荷を小さく抑え得ることとなる。   In addition, the annular gear of the planetary gear mechanism is in a fixed state, that is, the annular gear of the gear group constituting the planetary gear mechanism is in a fixed state. The inertial load can be kept small.

また、本発明の請求項２に係る二段変速機において、クラッチ機構の駆動部によりスライド筒を軸方向に移動させ、スライド筒の筒側係合部をキャリアのキャリア側係合部に係合させて高速モードにすると、入力軸に付与された回転出力がそのまま出力軸に伝達される。   Further, in the two-stage transmission according to claim 2 of the present invention, the slide cylinder is moved in the axial direction by the drive part of the clutch mechanism, and the cylinder side engaging part of the slide cylinder is engaged with the carrier side engaging part of the carrier. When the high-speed mode is selected, the rotational output applied to the input shaft is transmitted to the output shaft as it is.

一方、クラッチ機構の駆動部によりスライド筒を軸方向に移動させ、スライド筒の筒側係合部をキャリアのキャリア側係合部から離間させて低速モードに切り換えると、遊星歯車機構で減速された回転出力が出力軸に伝達される。   On the other hand, when the slide cylinder is moved in the axial direction by the drive unit of the clutch mechanism and the cylinder side engaging part of the slide cylinder is separated from the carrier side engaging part of the carrier and switched to the low speed mode, the speed is reduced by the planetary gear mechanism. The rotational output is transmitted to the output shaft.

つまり、入力軸に付与される回転出力を減速せずに出力軸に伝達する高速モードと、入力軸に付与される回転出力を減速して出力軸に伝達する低速モードとを切り換える際には、重量の嵩む摩擦クラッチを使用しないでクラッチ機構のスライド筒を軸方向に移動させるだけなので、その分だけ、より一層の小型軽量化及び構造の簡略化が図られることとなる。   In other words, when switching between the high speed mode in which the rotational output applied to the input shaft is transmitted to the output shaft without decelerating and the low speed mode in which the rotational output applied to the input shaft is decelerated and transmitted to the output shaft, Since only the slide cylinder of the clutch mechanism is moved in the axial direction without using a heavy friction clutch, the size and weight can be further reduced and the structure can be simplified accordingly.

さらに、本発明の請求項３に係る二段変速機において、キャリアのキャリア側係合部として、キャリアに固定された歯車軸の先端部を用いるので、キャリア側係合部を別に設ける場合と比べて、さらなる構造の簡略化が図られることとなる。   Furthermore, in the two-stage transmission according to claim 3 of the present invention, since the tip end portion of the gear shaft fixed to the carrier is used as the carrier-side engaging portion of the carrier, compared to the case where the carrier-side engaging portion is provided separately. As a result, the structure can be further simplified.

本発明に係る二段変速機では、小型軽量化に加えて構造の簡略化をも実現することが可能であるという非常に優れた効果がもたらされる。   In the two-speed transmission according to the present invention, a very excellent effect is achieved that it is possible to realize a simplified structure in addition to a reduction in size and weight.

本発明の一実施例による二段変速機の遊星歯車機構の歯車レイアウト説明図である。It is a gear layout explanatory drawing of the planetary gear mechanism of the two-stage transmission by one Example of this invention. 図１に示した二段変速機の低速モードにおける図１のＡ−Ａ線位置での断面説明図（ａ）及び図２（ａ）のＢ−Ｂ線位置での断面説明図（ｂ）である。FIG. 2 is a cross-sectional explanatory view at the position of the AA line in FIG. 1 in the low-speed mode of the two-stage transmission shown in FIG. 1 and a cross-sectional explanatory view at the position of the BB line in FIG. is there. 図１に示した二段変速機の高速モードにおける図１のＡ−Ａ線位置での断面説明図（ａ）及び図３（ａ）のＣ−Ｃ線位置での断面説明図（ｂ）である。FIG. 2 is a cross-sectional explanatory view at the position of the AA line in FIG. 1 in the high-speed mode of the two-stage transmission shown in FIG. 1 and a cross-sectional explanatory view at the position of the CC line in FIG. is there.

以下、本発明に係る二段変速機を図面に基づいて説明する。   Hereinafter, a two-stage transmission according to the present invention will be described with reference to the drawings.

図１〜図３は、本発明に係る二段変速機の一実施例を示している。   1 to 3 show an embodiment of a two-speed transmission according to the present invention.

図１〜図３に示すように、この二段変速機１は、入力軸２と、出力軸３と、遊星歯車機構１０を具備しており、入力軸２には図示しないモータの回転出力軸が連結され、出力軸３には図示しない例えば駆動車輪が接続される。   As shown in FIGS. 1 to 3, the two-stage transmission 1 includes an input shaft 2, an output shaft 3, and a planetary gear mechanism 10, and the input shaft 2 includes a rotation output shaft of a motor (not shown). Are coupled to the output shaft 3, for example, driving wheels (not shown).

遊星歯車機構１０は、入力軸２に一体で形成された太陽歯車１１と、この太陽歯車１１を囲んで配置される環状歯車１２と、太陽歯車１１及び環状歯車１２の双方に噛み合う複数個の遊星歯車１３と、出力軸３に固定されたキャリア１４を具備しており、環状歯車１２は、図示しない例えばケースに固定されている。キャリア１４には、遊星歯車１３を回転自在に支持する歯車軸１５の基端部１５ａが貫通状態で固定されており、遊星歯車機構１０は、入力軸２に付与されるモータからの回転出力を減速して出力するようになっている。   The planetary gear mechanism 10 includes a sun gear 11 formed integrally with the input shaft 2, an annular gear 12 disposed so as to surround the sun gear 11, and a plurality of planets meshing with both the sun gear 11 and the annular gear 12. A gear 13 and a carrier 14 fixed to the output shaft 3 are provided, and the annular gear 12 is fixed to a case (not shown), for example. A base end portion 15 a of a gear shaft 15 that rotatably supports the planetary gear 13 is fixed to the carrier 14 in a penetrating state, and the planetary gear mechanism 10 receives a rotation output from a motor applied to the input shaft 2. It decelerates and outputs.

また、この二段変速機１は、入力軸２に付与される回転出力を遊星歯車機構１０で落として出力軸３に出力する低速モードと、入力軸２に付与される回転出力を遊星歯車機構１０のキャリア１４を介して出力軸３にそのまま出力する高速モードとを切り換えるクラッチ機構２０を備えている。   The two-stage transmission 1 also includes a low speed mode in which the rotational output applied to the input shaft 2 is dropped by the planetary gear mechanism 10 and output to the output shaft 3, and the rotational output applied to the input shaft 2 is transmitted to the planetary gear mechanism. A clutch mechanism 20 for switching to a high speed mode in which the output is output to the output shaft 3 as it is via the ten carriers 14 is provided.

このクラッチ機構２０は、入力軸２に嵌合されたスライド筒２１を具備している。このスライド筒２１及び入力軸２には、互いに嵌め込んだ状態で係合する軸方向のスプライン２１ａ，２ａがそれぞれ形成されており、スライド筒２１は入力軸２に対して軸方向に移動可能で且つ回転不能に連結されている。   The clutch mechanism 20 includes a slide cylinder 21 fitted to the input shaft 2. The slide cylinder 21 and the input shaft 2 are formed with axial splines 21 a and 2 a that are engaged with each other in a state of being fitted to each other, and the slide cylinder 21 is movable in the axial direction with respect to the input shaft 2. And it is connected so that it cannot rotate.

この場合、クラッチ機構２０のスライド筒２１には、内向き凸部（筒側係合部）２１ｂが円周方向の３箇所に形成されており、一方、遊星歯車機構１０のキャリア１４には、スライド筒２１の内向き凸部２１ｂと互いに係合することで入力軸２の回転がこのキャリア１４にそのまま伝達されるキャリア側係合部が円周方向の３箇所に配置されており、この実施例では、キャリア１４に固定されて遊星歯車１３を回転自在に支持する３本の歯車軸１５の各先端部１５ｂがキャリア側係合部として機能するようになっている。   In this case, the slide cylinder 21 of the clutch mechanism 20 has inward convex portions (cylinder side engaging portions) 21b formed at three locations in the circumferential direction, while the carrier 14 of the planetary gear mechanism 10 has There are three carrier side engaging portions arranged in the circumferential direction in which the rotation of the input shaft 2 is transmitted to the carrier 14 as it is by engaging with the inwardly protruding portions 21b of the slide cylinder 21. In the example, the tip portions 15b of the three gear shafts 15 fixed to the carrier 14 and rotatably supporting the planetary gear 13 function as carrier-side engaging portions.

また、このクラッチ機構２０は、低速モードにおけるスライド筒２１の内向き凸部２１ｂが歯車軸１５の先端部１５ｂから離れる位置と、高速モードにおけるスライド筒２１の内向き凸部２１ｂが歯車軸１５の先端部１５ｂと係合する位置との間で該スライド筒２１を移動させる直動アクチュエータ（駆動部）２２を具備している。   In addition, the clutch mechanism 20 includes a position where the inward convex portion 21b of the slide cylinder 21 in the low speed mode is separated from the distal end portion 15b of the gear shaft 15, and the inward convex portion 21b of the slide cylinder 21 in the high speed mode. A linear motion actuator (drive unit) 22 that moves the slide cylinder 21 between a position where it engages with the distal end portion 15b is provided.

この直動アクチュエータ２２の押し引きロッド２２ａの先端には、スライド筒２１の外周面に形成された環状凸部２１ｃと相互に摺動自在に嵌合する凹状ブロック２２ｃが配置されており、直動アクチュエータ２２の押し引きロッド２２ａを押し引き動作させることで、スライド筒２１を入力軸２の軸方向に移動させるようになっている。   A concave block 22c that is slidably fitted to an annular convex portion 21c formed on the outer peripheral surface of the slide cylinder 21 is disposed at the distal end of the push-pull rod 22a of the linear actuator 22, The slide cylinder 21 is moved in the axial direction of the input shaft 2 by pushing and pulling the push-pull rod 22 a of the actuator 22.

なお、図２及び図３における符号２４は移動規制板であり、スライド筒２１が図示しないモータ側に移動し過ぎるのを規制している。また、図２における符号１６は必要に応じて装着される補強プレートであり、キャリア１４に固定された３本の歯車軸１５の各先端部１５ｂの位置ずれを回避する。   2 and 3 is a movement restricting plate that restricts the slide cylinder 21 from moving too far to the motor (not shown). Further, reference numeral 16 in FIG. 2 denotes a reinforcing plate that is attached as necessary, and avoids displacement of the tip portions 15 b of the three gear shafts 15 fixed to the carrier 14.

上記した二段変速機１を、例えば、電気自動車に搭載する場合、クラッチ機構２０の直動アクチュエータ２２にロッド押出し動作を行わせて、スライド筒２１を図２（ａ）左方向に移動させ、このスライド筒２１の内向き凸部２１ｂを歯車軸１５の先端部１５ｂに係合させて高速モードにすると、図３に示すように、入力軸２に付与された図外のモータからの回転出力がキャリア１４を介してそのまま出力軸３に伝達されることとなる。つまり、高速回転出力による電気自動車の走行が可能となる。   When the above-described two-stage transmission 1 is mounted on, for example, an electric vehicle, the linear actuator 22 of the clutch mechanism 20 performs a rod pushing operation to move the slide cylinder 21 in the left direction in FIG. When the inward convex portion 21b of the slide cylinder 21 is engaged with the tip portion 15b of the gear shaft 15 to enter the high speed mode, as shown in FIG. 3, the rotational output from the motor (not shown) applied to the input shaft 2 is obtained. Is transmitted to the output shaft 3 through the carrier 14 as it is. That is, the electric vehicle can be driven by high-speed rotation output.

一方、この高速モードにおいて、クラッチ機構２０の直動アクチュエータ２２にロッド引き込み動作を行わせて、スライド筒２１を図３（ａ）右方向に移動させ、このスライド筒２１の内向き凸部２１ｂを歯車軸１５の先端部１５ｂから離間させて低速モードにすると、図２に示すように、遊星歯車機構１０で減速されたモータからの回転出力が出力軸３に伝達されることとなる。つまり、低速回転出力による電気自動車の走行が可能となる。   On the other hand, in this high speed mode, the direct acting actuator 22 of the clutch mechanism 20 performs the rod pulling operation to move the slide cylinder 21 in the right direction in FIG. 3A, and the inward convex portion 21b of the slide cylinder 21 is moved. When separated from the tip 15b of the gear shaft 15 to the low speed mode, the rotational output from the motor decelerated by the planetary gear mechanism 10 is transmitted to the output shaft 3 as shown in FIG. That is, the electric vehicle can be driven by the low-speed rotation output.

このように、上記した二段変速機１では、減速されていない高速回転出力と、減速された低速回転出力とを一つのクラッチ機構２０によって選択的に切り換えて出力軸３に出力するようにしているので、重量の嵩む摩擦クラッチを複数組必要としない分だけ、小型軽量化が図られることとなる。   As described above, in the two-stage transmission 1 described above, the high-speed rotation output that is not decelerated and the low-speed rotation output that is decelerated are selectively switched by one clutch mechanism 20 and output to the output shaft 3. Therefore, the size and weight can be reduced by the amount that does not require a plurality of heavy friction clutches.

特に、高速モードでは、入力軸２に付与された回転出力を遊星歯車機構１０のキャリア１４を介して出力軸３にそのまま伝達するようにしているので、構造の簡略化も図られることとなる。   In particular, in the high-speed mode, the rotational output applied to the input shaft 2 is transmitted as it is to the output shaft 3 via the carrier 14 of the planetary gear mechanism 10, so that the structure can be simplified.

また、遊星歯車機構１０の環状歯車１２を図示しない例えばケースに固定している、すなわち、遊星歯車機構１０を構成する歯車群のうちの環状歯車１２を固定状態としているので、環状歯車１２が回転しない分だけ、高速回転出力時における慣性負荷を小さく抑え得ることとなる。   Further, the annular gear 12 of the planetary gear mechanism 10 is fixed to a case (not shown), for example, that is, the annular gear 12 of the gear group constituting the planetary gear mechanism 10 is in a fixed state, so that the annular gear 12 rotates. As a result, the inertia load at the time of high-speed rotation output can be kept small.

さらに、上記した二段変速機１において、入力軸２に付与される回転出力を減速しないで出力軸３に伝達する高速モードと、入力軸２に付与される回転出力を減速して出力軸３に伝達する低速モードとを切り換える際には、重量の嵩む摩擦クラッチを使用せずにクラッチ機構２０のスライド筒２１を軸方向に移動させるだけなので、その分だけ、より一層の小型軽量化及び構造の簡略化が図られることとなる。   Further, in the above-described two-stage transmission 1, the high-speed mode in which the rotational output applied to the input shaft 2 is transmitted to the output shaft 3 without decelerating, and the rotational output applied to the input shaft 2 is decelerated to reduce the output shaft 3 When switching to the low-speed mode transmitted to the vehicle, the slide cylinder 21 of the clutch mechanism 20 is merely moved in the axial direction without using a heavy friction clutch, so that further reduction in size and weight and structure are achieved. Is to be simplified.

さらに、上記した二段変速機１において、キャリア１４のキャリア側係合部として、キャリア１４に固定された歯車軸１５の先端部１５ｂを用いているので、キャリア側係合部を歯車軸１５の先端部１５ｂとは別に設ける場合と比べて、さらなる構造の簡略化が図られることとなる。   Further, in the above-described two-stage transmission 1, since the tip end portion 15b of the gear shaft 15 fixed to the carrier 14 is used as the carrier-side engaging portion of the carrier 14, the carrier-side engaging portion is used as the gear-side engaging portion of the gear shaft 15. Compared with the case where it is provided separately from the tip 15b, the structure can be further simplified.

上記した実施例では、本発明に係る二段変速機を電気自動車に搭載した場合を例に挙げて説明したが、これに限定されるものではなく、例えば、本発明に係る二段変速機を工作機械の変速機として採用してもよい。   In the above-described embodiment, the case where the two-stage transmission according to the present invention is mounted on an electric vehicle has been described as an example. However, the present invention is not limited to this. For example, the two-stage transmission according to the present invention is not limited to this. You may employ | adopt as a transmission of a machine tool.

本発明に係る二段変速機の構成は、上記した実施例に限定されるものではなく、他の構成として、例えば、キャリア側係合部を補強プレート１６に一体又は別体で配置するようにしてもよい。   The configuration of the two-speed transmission according to the present invention is not limited to the above-described embodiment. As another configuration, for example, the carrier side engaging portion is arranged integrally or separately on the reinforcing plate 16. May be.

１ 二段変速機
２ 入力軸
３ 出力軸
１０ 遊星歯車機構
１１ 太陽歯車
１２ 環状歯車
１３ 遊星歯車
１４ キャリア
１５ 歯車軸
１５ｂ 歯車軸の先端部（キャリア側係合部）
２０ クラッチ機構
２１ スライド筒
２１ｂ 内向き凸部（筒側係合部）
２２ 直動アクチュエータ（駆動部） 1 Two-speed transmission 2 Input shaft 3 Output shaft
DESCRIPTION OF SYMBOLS 10 Planetary gear mechanism 11 Sun gear 12 Ring gear 13 Planetary gear 14 Carrier 15 Gear shaft 15b The front-end | tip part (carrier side engaging part) of a gear shaft
20 Clutch mechanism 21 Slide cylinder 21b Inward convex part (cylinder side engaging part)
22 Linear Actuator (Driver)

Claims (3)

入力軸と、
出力軸と、
前記入力軸と同軸回転する太陽歯車と、この太陽歯車を囲んで配置される環状歯車と、前記太陽歯車及び環状歯車の双方に噛み合う遊星歯車と、前記出力軸に固定されて前記遊星歯車を回転自在に支持することで前記入力軸に付与される回転出力を落として出力するキャリアを具備した遊星歯車機構を備え、
前記遊星歯車機構の環状歯車を固定状態とし、
前記入力軸に付与される回転出力を前記遊星歯車機構で落として前記出力軸に出力する低速モードと、前記入力軸に付与される回転出力を前記遊星歯車機構の前記キャリアを介して前記出力軸にそのまま出力する高速モードとを切り換えるクラッチ機構を設けた
ことを特徴とする二段変速機。 An input shaft;
An output shaft;
A sun gear rotating coaxially with the input shaft, an annular gear arranged around the sun gear, a planetary gear meshing with both the sun gear and the annular gear, and rotating the planetary gear fixed to the output shaft Comprising a planetary gear mechanism having a carrier for dropping and outputting the rotational output applied to the input shaft by freely supporting,
The annular gear of the planetary gear mechanism is in a fixed state,
A low speed mode in which the rotational output applied to the input shaft is dropped by the planetary gear mechanism and output to the output shaft, and the rotational output applied to the input shaft is output to the output shaft via the carrier of the planetary gear mechanism. A two-stage transmission characterized in that a clutch mechanism is provided for switching between a high-speed mode and an output as it is. 前記クラッチ機構は、
前記入力軸に軸方向に移動可能で且つ回転不能に嵌合されたスライド筒と、
前記入力軸に嵌合された前記スライド筒に配置された筒側係合部と、
前記遊星歯車機構の前記遊星歯車を回転自在に支持する前記キャリアに配置されて、前記スライド筒の前記筒側係合部と互いに係合することで前記入力軸の回転が該キャリアにそのまま伝達されるキャリア側係合部と、
前記低速モードにおける前記スライド筒の前記筒側係合部が前記キャリアの前記キャリア側係合部から離れた位置、及び、前記高速モードにおける前記スライド筒の前記筒側係合部が前記キャリアの前記キャリア側係合部と係合する位置の間で該スライド筒を移動させる駆動部を具備している請求項１に記載の二段変速機。 The clutch mechanism is
A slide cylinder that is axially movable and non-rotatably fitted to the input shaft;
A cylinder side engaging portion disposed on the slide cylinder fitted to the input shaft;
The rotation of the input shaft is transmitted to the carrier as it is by being arranged on the carrier that rotatably supports the planetary gear of the planetary gear mechanism and engaging with the cylinder side engaging portion of the slide cylinder. A carrier side engaging portion,
The position where the cylinder side engaging portion of the slide cylinder is separated from the carrier side engaging section of the carrier in the low speed mode, and the cylinder side engaging portion of the slide cylinder in the high speed mode is the position of the carrier. The two-stage transmission according to claim 1, further comprising a drive unit that moves the slide cylinder between positions engaged with the carrier side engagement unit. 前記キャリアの前記キャリア側係合部は、前記キャリアに固定されて前記遊星歯車機構の前記遊星歯車を回転自在に支持する歯車軸の先端部である請求項２に記載の二段変速機。   The two-stage transmission according to claim 2, wherein the carrier side engaging portion of the carrier is a tip portion of a gear shaft fixed to the carrier and rotatably supporting the planetary gear of the planetary gear mechanism.
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JP6545921B1 (en) * 2018-06-02 2019-07-17 ユニプレス株式会社 Two-speed transmission for electric vehicles
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