JP5621575B2 - Transmission method of transmission using non-circular gear pair - Google Patents

Transmission method of transmission using non-circular gear pair Download PDF

Info

Publication number
JP5621575B2
JP5621575B2 JP2010282040A JP2010282040A JP5621575B2 JP 5621575 B2 JP5621575 B2 JP 5621575B2 JP 2010282040 A JP2010282040 A JP 2010282040A JP 2010282040 A JP2010282040 A JP 2010282040A JP 5621575 B2 JP5621575 B2 JP 5621575B2
Authority
JP
Japan
Prior art keywords
gear pair
circular gear
reduction ratio
clutch
input member
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.)
Expired - Fee Related
Application number
JP2010282040A
Other languages
Japanese (ja)
Other versions
JP2012127483A (en
Inventor
雅晴 小森
雅晴 小森
英隆 古賀
英隆 古賀
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Isuzu Motors Ltd
Kyoto University
Original Assignee
Isuzu Motors Ltd
Kyoto University
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Isuzu Motors Ltd, Kyoto University filed Critical Isuzu Motors Ltd
Priority to JP2010282040A priority Critical patent/JP5621575B2/en
Publication of JP2012127483A publication Critical patent/JP2012127483A/en
Application granted granted Critical
Publication of JP5621575B2 publication Critical patent/JP5621575B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Structure Of Transmissions (AREA)

Description

本発明は非円形歯車対を用いた変速機の変速方法に関し、詳しくは、減速比を切り替える際に非円形歯車対を用いた変速機の変速方法に関する。   The present invention relates to a transmission method for a transmission that uses a non-circular gear pair, and more particularly to a transmission method for a transmission that uses a non-circular gear pair when switching a reduction ratio.

なお、本明細書中において、「減速比」は、駆動側回転速度／被動側回転速度（あるいは、入力側回転速度／出力側回転速度）で表され、駆動側回転速度よりも被動側回転速度の方が小さくなる場合（いわゆる減速の場合）には１より大きい値となる。「減速比」は、駆動側回転速度よりも被動側回転速度の方が大きい場合（いわゆる増速の場合）についても同じ定義を用いて表し、この場合には、１より小さい値となる。   In this specification, the “reduction ratio” is represented by the drive side rotational speed / driven side rotational speed (or the input side rotational speed / output side rotational speed), and the driven side rotational speed rather than the drive side rotational speed. When is smaller (so-called deceleration), the value is larger than 1. The “reduction ratio” is expressed using the same definition when the driven side rotational speed is larger than the driving side rotational speed (so-called speed increase). In this case, the “reduction ratio” is a value smaller than 1.

従来、入力軸と出力軸との間に連結する歯車対を切り替えることにより減速比を変える一般の変速機では、減速比を切り替える際にいずれの歯車対も入力軸と出力軸との間に連結されていない状態があり、このときには動力が伝達されない。そこで、減速比を切り替える際に過渡的に非円形歯車対を入力軸と出力軸との間に連結することにより、減速比を切り替える際も連続して動力が伝達されるようにすることができる、非円形歯車対を備えた変速機が提案されている。   Conventionally, in a general transmission that changes the reduction ratio by switching the gear pair connected between the input shaft and the output shaft, when changing the reduction ratio, both gear pairs are connected between the input shaft and the output shaft. There is a state that is not done, at this time the power is not transmitted. Therefore, when the reduction ratio is switched, a non-circular gear pair is transiently connected between the input shaft and the output shaft, so that power can be continuously transmitted even when the reduction ratio is switched. A transmission with a non-circular gear pair has been proposed.

例えば、変速機は、減速比ＲＨの歯車対と、減速比ＲＬの歯車対と、減速比がＲＨとＲＬを含む範囲で変化する非円形歯車対とを、それぞれ、クラッチを用いて入力軸と出力軸との間に解除可能に連結できるように構成にする。この変速機を用いて、減速比をＲＨからＲＬに変える場合、図１０に示すようにクラッチを動作させる。 For example, the transmission uses a clutch with a gear pair with a reduction ratio RH, a gear pair with a reduction ratio RL , and a non-circular gear pair with a reduction ratio changing in a range including RH and RL , respectively. The input shaft and the output shaft can be releasably connected. When the reduction ratio is changed from RH to RL using this transmission, the clutch is operated as shown in FIG.

図１０（ａ）は、非円形歯車対の減速比を模式的に示すグラフである。横軸は入力軸の回転角度、縦軸は非円形歯車対の減速比である。図１０（ｂ）の表は、クラッチのＯＮの状態を○印で示し、ＯＦＦの状態は空欄としている。減速比ＲＨの歯車対のクラッチを「クラッチ（ＲＨ）」、減速比ＲＬの歯車対のクラッチを「クラッチ（ＲＬ）」、減速比が変化する非円形歯車対のクラッチを「クラッチ（変速）」と表している。 FIG. 10A is a graph schematically showing a reduction ratio of a non-circular gear pair. The horizontal axis represents the rotation angle of the input shaft, and the vertical axis represents the reduction ratio of the non-circular gear pair. In the table of FIG. 10B, the ON state of the clutch is indicated by a circle, and the OFF state is blank. The clutch of the gear pair with the reduction ratio RH is “clutch (R H )”, the clutch of the gear pair with the reduction ratio RL is “clutch (R L )”, and the clutch of the non-circular gear pair with the changing reduction ratio is “clutch” (Speed change) ".

図１０に示すように、減速比ＲＨの歯車対のクラッチのみがＯＮであり、減速比がＲＨである状態で、非円形歯車対の減速比が一定の減速比ＲＨとなる区間３０２に入ったら、減速比が変化する非円形歯車対のクラッチをＯＮにする。非円形歯車対のクラッチをＯＮにするとき、減速比ＲＨの歯車対のクラッチは、ＯＮのままである。 As shown in FIG. 10, in a state where only the clutch of the gear pair having the reduction ratio RH is ON and the reduction ratio is RH , the section 302 in which the reduction ratio of the non-circular gear pair becomes a constant reduction ratio RH. When entering, the clutch of the non-circular gear pair whose reduction ratio changes is turned ON. When the clutch of the non-circular gear pair is turned on, the clutch of the gear pair having the reduction ratio RH remains on.

次いで、区間３０２において非円形歯車対のクラッチがＯＮになった後、かつ、非円形歯車対の減速比がＲＨからＲＬに変化する区間３０３に入る前に、減速比ＲＨの歯車対のクラッチをＯＦＦにする。 Next, after the clutch of the non-circular gear pair is turned on in the section 302 and before entering the section 303 where the reduction ratio of the non-circular gear pair changes from RH to RL , the gear pair having the reduction ratio RH is used. Turn off the clutch.

次いで、非円形歯車対のクラッチのみがＯＮの状態で、非円形歯車対の減速比がＲＨからＲＬに変化する区間３０３を通過した後、一定の減速比ＲＬとなる区間３０４に入ったら、減速比ＲＬの歯車対のクラッチをＯＮにする。減速比ＲＬの歯車対のクラッチをＯＮにするとき、非円形歯車対のクラッチはＯＮのままである。 Next, in a state where only the clutch of the non-circular gear pair is ON, after passing through the section 303 where the reduction ratio of the non-circular gear pair changes from RH to RL , the section 304 where the constant reduction ratio RL is entered. Then, the clutch of the gear pair with the reduction ratio RL is turned on. When the clutch of the gear pair having the reduction ratio RL is turned on, the clutch of the non-circular gear pair remains on.

次いで、区間３０４において減速比ＲＬのクラッチがＯＮになった後、かつ、非円形歯車対の減速比がＲＬからＲＨに変化する区間３０５に入る前に、非円形歯車対のクラッチをＯＦＦにする。これにより、入力軸と出力軸との間に減速比ＲＬの歯車対のみが連結された状態になり、入力軸と出力軸との間の減速比は一定の減速比ＲＬとなる（例えば、特許文献１参照）。 Next, after the clutch of the reduction ratio RL is turned ON in the section 304 and before entering the section 305 where the reduction ratio of the non-circular gear pair changes from RL to RH , the clutch of the non-circular gear pair is engaged. Turn off. As a result, only the gear pair having the reduction ratio RL is connected between the input shaft and the output shaft, and the reduction ratio between the input shaft and the output shaft becomes a constant reduction ratio RL (for example, , See Patent Document 1).

国際公開第２００８／０６２７１８号International Publication No. 2008/062718

上述した非円形歯車対を備えた変速機において、歯車対及び非円形歯車対のクラッチには、効率よく動力を伝達できる噛み合いクラッチを用いることが好ましい。   In the transmission including the above-described non-circular gear pair, it is preferable to use a meshing clutch capable of efficiently transmitting power as the clutch of the gear pair and the non-circular gear pair.

しかし、図１０に示したように、区間３０２，３０４において、ＯＮ／ＯＦＦを切り替える歯車対のクラッチと非円形歯車対のクラッチとの２つのクラッチを同時にＯＮにする場合、２つのクラッチのうち、後でＯＮになるクラッチについては、駆動側と被動側のクラッチ歯の位相を一致させる必要がある。しかも、減速比の切り替えを繰り返しても位相を一致させる必要がある。このため、クラッチの設計や、歯車対及び非円形歯車対の歯車の設計において制約が生じ、設計の自由度が低下し、最適な性能となるクラッチや歯車を備えた変速機の実現が困難となる場合がある。   However, as shown in FIG. 10, in the sections 302 and 304, when the two clutches, the clutch of the gear pair that switches ON / OFF and the clutch of the non-circular gear pair, are simultaneously turned on, of the two clutches, For clutches that are to be turned on later, it is necessary to match the phases of the clutch teeth on the drive side and the driven side. Moreover, it is necessary to make the phases coincide even if the reduction ratio is repeatedly switched. For this reason, restrictions are imposed on the design of the clutch and the gears of the gear pair and the non-circular gear pair, the degree of freedom in design is reduced, and it is difficult to realize a transmission having a clutch and gears that have optimum performance. There is a case.

本発明は、かかる実情に鑑み、クラッチや歯車の設計の自由度を高くでき、最適な性能となるクラッチや歯車を備えた変速機を実現しやすい、非円形歯車対を用いた変速機の変速方法を提供しようとするものである。   In view of such circumstances, the present invention can increase the degree of freedom in designing clutches and gears, and can easily realize a transmission equipped with clutches and gears with optimal performance. Is to provide a method.

本発明は、上記課題を解決するために、以下のように構成した、非円形歯車対を用いた変速機の変速方法を提供する。   In order to solve the above-mentioned problems, the present invention provides a speed change method for a transmission using a non-circular gear pair configured as follows.

非円形歯車対を用いた変速機の変速方法は、（ａ）回転可能に支持された入力部材と、（ｂ）回転可能に支持された出力部材と、（ｃ）前記入力部材と前記出力部材との間にそれぞれ配置され、前記入力部材と前記出力部材との間に連結されたときの減速比が一定である、少なくとも２つの歯車対と、（ｄ）前記入力部材と前記出力部材との間に、少なくとも２つの前記歯車対を、それぞれ、ＯＮのときに連結し、ＯＦＦのときに連結を解除する、少なくとも２つクラッチと、（ｅ）前記入力部材と前記出力部材との間に配置され、前記入力部材と前記出力部材との間に連結されたときの減速比が変動する、少なくとも１つの非円形歯車対と、（ｆ）前記入力部材と前記出力部材との間に前記非円形歯車対を、ＯＮのときに連結し、ＯＦＦのときに連結を解除する、少なくとも１つの非円形歯車対用クラッチとを備え、前記非円形歯車対は、前記入力部材と前記出力部材との間に前記非円形歯車対が連結され、前記非円形歯車対の一方が１回転し、前記非円形歯車対の他方が１回転以上回転して前記非円形歯車対の噛み合いが一巡するときに、（ｉ）前記非円形歯車対の噛み合いにより前記入力部材と前記出力部材との間の減速比が、前記入力部材と前記出力部材との間に少なくとも２つの前記歯車対がそれぞれ連結されたときの前記入力部材と前記出力部材との間の減速比と同じになる、少なくとも２つの定速噛み合い区間と、（ii）隣り合う前記定速噛み合い区間の間において、前記非円形歯車対の噛み合いにより前記入力部材と前記出力部材との間の減速比が、隣り合う前記定速噛み合い区間の一方の減速比から隣り合う前記定速噛み合い区間の他方の減速比まで変化する、少なくとも２つの変速噛み合い区間とを含む、変速機を用いる。前記入力部材と前記出力部材との間に１つの前記歯車対のみが連結された第１の状態から、前記入力部材と前記出力部材との間に前記非円形歯車対のみが連結され前記変速噛み合い区間で噛み合う中間状態を経て、前記入力部材と前記出力部材との間に他の一つの前記歯車対のみが連結された第２の状態に切り替えることにより、回転する前記入力部材と前記出力部材との間の減速比を切り替える際に、前記非円形歯車対が前記定速噛み合い区間で噛み合い、前記入力部材と前記出力部材の間に前記歯車対を連結する場合の前記入力部材と前記出力部材との間の減速比と前記入力部材と前記出力部材の間に前記非円形歯車対を連結する場合の前記入力部材と前記出力部材との間の減速比とが同一であり、当該歯車対用の前記クラッチと当該非円形歯車対用の前記非円形歯車対用クラッチのいずれか一方がＯＮであり、かつ、他方がＯＦＦである状態から、前記一方をＯＦＦにした後に前記他方をＯＮにする工程を含み、前記他方は、位相が合う方向に駆動側と被動側が相対移動可能であれば駆動側と被動側の位相がずれていてもＯＮにすることができる噛み合いクラッチである。   A transmission method using a non-circular gear pair includes: (a) an input member that is rotatably supported; (b) an output member that is rotatably supported; and (c) the input member and the output member. And at least two gear pairs having a constant reduction ratio when connected between the input member and the output member, and (d) between the input member and the output member. In between, at least two of the gear pairs are connected between the input member and the output member, respectively, at least two clutches that are connected when ON and are disconnected when OFF. And at least one non-circular gear pair in which a reduction ratio when connected between the input member and the output member varies, and (f) the non-circular shape between the input member and the output member. The gear pair is connected when ON, and OFF At least one non-circular gear pair clutch for releasing the connection, wherein the non-circular gear pair is connected to the non-circular gear pair between the input member and the output member. When one of the gear pairs rotates one time and the other of the non-circular gear pairs rotates one or more times, and the meshing of the non-circular gear pair makes a complete cycle, (i) the input member is engaged by the meshing of the non-circular gear pair. The reduction ratio between the input member and the output member is a reduction ratio between the input member and the output member when at least two gear pairs are connected between the input member and the output member, respectively. At least two constant speed meshing sections that are the same, and (ii) between the adjacent constant speed meshing sections, the reduction ratio between the input member and the output member due to meshing of the non-circular gear pair is: Adjacent said constant A transmission is used that includes at least two speed change meshing sections that change from one speed reduction ratio of the fast meshing section to the other speed reduction ratio of the adjacent constant speed meshing section. From the first state in which only one gear pair is connected between the input member and the output member, only the non-circular gear pair is connected between the input member and the output member, and the speed change meshing is performed. By switching to a second state in which only one other pair of gears is connected between the input member and the output member through an intermediate state that meshes in a section, the input member and the output member that rotate The non-circular gear pair meshes in the constant speed meshing section, and the input member and the output member are connected when the gear pair is coupled between the input member and the output member. A reduction ratio between the input member and the output member when the non-circular gear pair is connected between the input member and the output member is the same, and The clutch and the non- Including a step of turning one of the non-circular gear pair clutches for the shape gear pair on and turning the other on from the state in which the other is turned off. Is a meshing clutch that can be turned on even if the driving side and the driven side are out of phase as long as the driving side and the driven side can move relative to each other in the phase matching direction.

上記方法によれば、非円形歯車対が定速噛み合い区間で噛み合い、歯車対と非円形歯車対の減速比が同一である間に、歯車対用と非円形歯車対用の２つのクラッチを同時にＯＮにしないので、２つのクラッチのうち、後でＯＮとなる他方のクラッチは、駆動側と被動側の位相がずれていても噛み合わせことができ、駆動側と被動側の位相を一致させる必要がない。このため、クラッチや歯車の設計の自由度を高くでき、最適な性能となる噛み合いクラッチや歯車を実現しやすくなる。   According to the above method, while the non-circular gear pair meshes in the constant speed meshing section and the reduction ratio of the gear pair and the non-circular gear pair is the same, the two clutches for the gear pair and the non-circular gear pair are simultaneously engaged. Since it is not turned on, the other clutch that is turned on later of the two clutches can be engaged even if the phases of the driving side and the driven side are shifted, and the phases of the driving side and the driven side must be matched. There is no. Therefore, the degree of freedom in designing the clutch and the gear can be increased, and it becomes easy to realize the meshing clutch and the gear having the optimum performance.

好ましい一態様において、前記クラッチがＯＮであるときに、前記入力部材と前記出力部材との間に連結された前記歯車対と減速比が一致する前記定速噛み合い区間で前記非円形歯車対が噛み合っている間に前記クラッチをＯＦＦにした後、前記非円形歯車対用クラッチをＯＮにすることにより、前記第１の状態から前記中間状態に切り替える。   In a preferred aspect, when the clutch is ON, the non-circular gear pair meshes in the constant speed meshing section in which the reduction ratio matches the gear pair coupled between the input member and the output member. After the clutch is turned off, the non-circular gear pair clutch is turned on to switch from the first state to the intermediate state.

この場合、非円形歯車対用クラッチを、噛み合いクラッチにすることができる。   In this case, the non-circular gear pair clutch can be a meshing clutch.

好ましい他の態様において、前記クラッチがＯＮであるならば前記入力部材と前記出力部材との間に連結される前記歯車対の減速比と一致する前記定速噛み合い区間で前記非円形歯車対が噛み合っている間に前記非円形歯車対用クラッチをＯＦＦにした後に、前記クラッチをＯＮにすることにより、前記中間状態から前記第２の状態に切り替える。   In another preferred aspect, if the clutch is ON, the non-circular gear pair meshes in the constant speed meshing section that matches the reduction ratio of the gear pair coupled between the input member and the output member. In the meantime, after the non-circular gear pair clutch is turned off, the clutch is turned on to switch the intermediate state to the second state.

この場合、クラッチを、噛み合いクラッチにすることができる。   In this case, the clutch can be a meshing clutch.

好ましくは、前記入力部材と前記出力部材とは、それぞれ、第１部分と第２部分とを含む。前記歯車対は、前記入力部材の前記第１部分と前記出力部材の前記第１部分との間に配置される。前記非円形歯車対は、前記入力部材の前記第２部分と前記出力部材の前記第２部分との間に配置される。前記変速機は、（ａ）前記入力部材の前記第１部分と前記入力部材の前記第２部分とを回転伝達可能に結合する第１の増減速装置と、（ｂ）前記出力部材の前記第１部分と前記出力部材の前記第２部分とを回転伝達可能に結合する第２の増減速装置とをさらに備える。前記非円形歯車対用クラッチは、前記第１の増減速装置と前記入力部材の前記第２部分と前記非円形歯車対と前記出力部材の前記第２部分と前記第２の増減速装置とを介して前記入力部材の前記第１部分と前記出力部材の前記第１部分との間を解除可能に連結する。前記非円形歯車対は、前記入力部材の前記第１部分と前記出力部材の前記第１部分との間に前記非円形歯車対が連結される。前記非円形歯車対の一方が１回転し、前記非円形歯車対の他方が１回転以上回転して前記非円形歯車対の噛み合いが一巡するときに、（ａ）前記定速噛み合い区間において、前記非円形歯車対の噛み合いにより前記入力部材の前記第１部分と前記出力部材の前記第１部分との間の減速比が、前記入力部材の前記第１部分と前記出力部材の前記第１部分との間に前記歯車対が連結されたときの前記入力部材の前記第１部分と前記出力部材の前記第１部分との間の減速比と同じになり、（ｂ）前記変速噛み合い区間において、前記非円形歯車対の噛み合いにより前記入力部材の前記第１部分と前記出力部材の前記第１部分との間の減速比が、隣り合う前記定速噛み合い区間の一方の減速比から隣り合う前記定速噛み合い区間の他方の減速比まで変化する。   Preferably, the input member and the output member each include a first portion and a second portion. The gear pair is disposed between the first portion of the input member and the first portion of the output member. The non-circular gear pair is disposed between the second portion of the input member and the second portion of the output member. The transmission includes: (a) a first speed increasing / decreasing device that couples the first part of the input member and the second part of the input member so as to be able to transmit rotation; and (b) the first part of the output member. And a second speed increasing / decreasing device that couples the first portion and the second portion of the output member so as to be capable of transmitting rotation. The non-circular gear pair clutch includes the first speed increasing / decreasing device, the second portion of the input member, the non-circular gear pair, the second portion of the output member, and the second speed increasing / decreasing device. The first part of the input member and the first part of the output member are releasably connected to each other. In the non-circular gear pair, the non-circular gear pair is connected between the first portion of the input member and the first portion of the output member. When one of the non-circular gear pairs rotates one time and the other of the non-circular gear pairs rotates one or more times, and the meshing of the non-circular gear pair makes a round, (a) in the constant speed meshing section, The reduction ratio between the first portion of the input member and the first portion of the output member due to the engagement of the non-circular gear pair is such that the first portion of the input member and the first portion of the output member are Between the first portion of the input member and the first portion of the output member when the pair of gears is connected, and (b) in the shift meshing section, Due to the meshing of the non-circular gear pair, the speed reduction ratio between the first part of the input member and the first part of the output member is adjacent to the constant speed adjacent to the one speed reduction ratio of the adjacent constant speed meshing section. Change to the other reduction ratio of the meshing section To.

この場合、増減速装置により、入力部材の第１部分と出力部材の第１部分との間に連結する歯車対を切り換える際に、非円形歯車対が入力部材の第２部分と出力部材の第２部分との間に連結されている時間を長く（又は、短く）することができ、それに伴って、クラッチを作動させる時間を長く（又は、減速比の切り替えに要する時間を短く）することができる。   In this case, when the gear pair connected between the first portion of the input member and the first portion of the output member is switched by the speed increasing / decreasing device, the non-circular gear pair is connected to the second portion of the input member and the first portion of the output member. The time connected between the two parts can be lengthened (or shortened), and accordingly, the time for operating the clutch can be lengthened (or the time required for switching the reduction ratio) can be shortened. it can.

入力が高速回転であっても、適宜な減速比の増減速装置により非円形歯車対の回転を遅くすることで、クラッチの切り換え動作をすべき時間を長くすることができるので、容易に減速比を変えることができる。入力が低速回転である場合には、適宜な減速比の増減速装置により非円形歯車対の回転を速くすることで、減速比の切り換えに要する時間を短縮することができる。   Even if the input is high-speed rotation, it is possible to lengthen the time for the clutch switching operation by slowing the rotation of the non-circular gear pair with an increase / decrease device with an appropriate reduction ratio. Can be changed. When the input is a low-speed rotation, the time required for switching the reduction ratio can be shortened by speeding up the rotation of the non-circular gear pair with an increase / decrease device having an appropriate reduction ratio.

また、非円形歯車対の設計の自由度を高くできる。   Further, the degree of freedom in designing the non-circular gear pair can be increased.

本発明によれば、クラッチや歯車の設計の自由度を高くでき、最適な性能となるクラッチや歯車を備えた変速機を実現しやすくなる。   ADVANTAGE OF THE INVENTION According to this invention, the freedom degree of design of a clutch and a gear can be made high, and it becomes easy to implement | achieve the transmission provided with the clutch and gear which become the optimal performance.

変速機の構成を模式的に示す機構図である。（実施例１）It is a mechanism figure showing the composition of a transmission typically. Example 1 変速機のクラッチの要部構成図である。（実施例１）It is a principal part block diagram of the clutch of a transmission. Example 1 変速機の歯車のピッチ円あるいはピッチ曲線を模式的に示す図である。（実施例１）It is a figure which shows typically the pitch circle or pitch curve of the gear of a transmission. Example 1 （ａ）非円形歯車対の減速比を模式的に示すグラフ、（ｂ）クラッチのＯＮとＯＦＦを示す表である。（実施例１）(A) The graph which shows typically the reduction ratio of a non-circular gear pair, (b) It is a table | surface which shows ON and OFF of a clutch. Example 1 （ａ）非円形歯車対の減速比を模式的に示すグラフ、（ｂ）クラッチのＯＮとＯＦＦを示す表である。（実施例１）(A) The graph which shows typically the reduction ratio of a non-circular gear pair, (b) It is a table | surface which shows ON and OFF of a clutch. Example 1 変速機の構成を示す断面図である。（実施例１）It is sectional drawing which shows the structure of a transmission. Example 1 変速機の動作を示す断面図である。（実施例１）It is sectional drawing which shows operation | movement of a transmission. Example 1 変速機の動作を示す断面図である。（実施例１）It is sectional drawing which shows operation | movement of a transmission. Example 1 変速機の構成を模式的に示す機構図である。（実施例２）It is a mechanism figure showing the composition of a transmission typically. (Example 2) （ａ）非円形歯車対の減速比を模式的に示すグラフ、（ｂ）クラッチのＯＮとＯＦＦを示す表である。（従来例）(A) The graph which shows typically the reduction ratio of a non-circular gear pair, (b) It is a table | surface which shows ON and OFF of a clutch. (Conventional example)

以下、本発明の実施の形態について、図１〜図９を参照しながら説明する。   Hereinafter, embodiments of the present invention will be described with reference to FIGS.

＜実施例１＞ 実施例１について、図１〜図８を参照しながら説明する。   <Example 1> Example 1 will be described with reference to FIGS.

まず、実施例１で用いる変速機１０の基本的な構成について、図１〜図３を参照しながら説明する。   First, a basic configuration of the transmission 10 used in the first embodiment will be described with reference to FIGS.

図１は、変速機１０の構成を模式的に示す機構図である。図１に示すように、変速機１０は、回転可能に支持されている入力軸１２及び出力軸１４と、第１の歯車対１６と、第２の歯車対１７と、非円形歯車対１８と、クラッチ４０，４２，４４とを備えている。   FIG. 1 is a mechanism diagram schematically showing the configuration of the transmission 10. As shown in FIG. 1, the transmission 10 includes an input shaft 12 and an output shaft 14 that are rotatably supported, a first gear pair 16, a second gear pair 17, and a non-circular gear pair 18. , Clutches 40, 42, and 44 are provided.

歯車対１６，１７及び非円形歯車対１８は、それぞれ、一対の歯車２０，３０；２２，３２；２４，３４が噛み合い、回転角度の遅れがない。すなわち、回転角度を正確に伝達し、かつ動力を効率的に伝達する。   In the gear pair 16, 17 and the non-circular gear pair 18, the pair of gears 20, 30; 22, 32; 24, 34 are engaged with each other, and there is no delay in the rotation angle. That is, the rotation angle is accurately transmitted and power is efficiently transmitted.

入力軸１２には、歯車対１６，１７及び非円形歯車対１８の一方の歯車（入力側歯車）２０，２２，２４が固定され、これらの歯車２０，２２，２４は入力軸１２と一体となって回転する。   One gear (input side gears) 20, 22, 24 of the gear pair 16, 17 and the non-circular gear pair 18 is fixed to the input shaft 12, and these gears 20, 22, 24 are integrated with the input shaft 12. Turns and turns.

出力軸１４には、歯車対１６，１７及び非円形歯車対１８の他方の歯車（出力側歯車）３０，３２，３４が、相対回転可能な状態に支持されている。出力側歯車３０，３２，３４は、クラッチ４０，４２，４４により、選択的に出力軸１４に結合される。すなわち、クラッチ４０，４２，４４がつながっているＯＮのときには、対応する出力側歯車３０，３２，３４は出力軸１４に対して結合され、結合された出力側歯車３０，３２，３４と出力軸１４とは一体となって回転する。クラッチ４０，４２，４４が切れているＯＦＦのときには、出力側歯車３０，３２，３４は、出力軸１４の軸方向の移動が拘束されながら、出力軸１４に対して相対回転可能となる。   On the output shaft 14, the other gears (output side gears) 30, 32, 34 of the gear pair 16, 17 and the non-circular gear pair 18 are supported in a relatively rotatable state. The output side gears 30, 32 and 34 are selectively coupled to the output shaft 14 by clutches 40, 42 and 44. That is, when the clutches 40, 42, 44 are ON, the corresponding output side gears 30, 32, 34 are coupled to the output shaft 14, and the coupled output side gears 30, 32, 34 and the output shaft are coupled. 14 and rotate together. When the clutches 40, 42, 44 are OFF, the output side gears 30, 32, 34 can rotate relative to the output shaft 14 while restraining the movement of the output shaft 14 in the axial direction.

クラッチ４０，４２，４４がＯＮのとき、クラッチ４０，４２，４４での滑り等がなければ、クラッチ４０，４２，４４がＯＮとなっている出力側歯車３０，３２，３４から出力軸１４に、回転角度を正確に伝達し、かつ動力を効率的に伝達することができる。   When the clutches 40, 42, and 44 are ON, if there is no slippage or the like at the clutches 40, 42, and 44, the output side gears 30, 32, and 34 where the clutches 40, 42, and 44 are ON are changed to the output shaft 14. The rotation angle can be accurately transmitted, and the power can be transmitted efficiently.

クラッチ４０，４２，４４には、ドグクラッチ、ジョークラッチ、歯形クラッチ等の噛み合いクラッチを用いる。円板クラッチ、ドラムクラッチなどの摩擦クラッチでは滑りが発生する可能性がある。これに対して、噛み合いクラッチは、駆動側と被動側とに形成された突起や穴等の機械的構造が噛み合い、摩擦クラッチのような滑りが発生しないので、回転角度を極めて正確に伝達し、かつ動力を極めて効率的に伝達することができるからである。   As the clutches 40, 42, and 44, meshing clutches such as dog clutches, jaw clutches, and tooth-shaped clutches are used. Sliding may occur in friction clutches such as disc clutches and drum clutches. On the other hand, the meshing clutch meshes mechanical structures such as protrusions and holes formed on the driving side and the driven side, and does not generate slipping like a friction clutch, so transmits the rotation angle very accurately, This is because power can be transmitted very efficiently.

クラッチ４０，４２，４４には、例えば図２に示す噛み合いクラッチ４８を用いる。図２は噛み合いクラッチ４８の構成を模式的に示す要部構成図である。図２に示すように、噛み合いクラッチ４８は、駆動側４８ｓと被動側４８ｔとが軸方向に互いに対向するように配置され、互いに対向する側面に、突起形状のクラッチ歯４８ｐ，４８ｑが間欠的に設けられている。被動側４８ｔと駆動側４８ｓは、いずれか一方又は両方が軸方向に移動し、互いに接離する。   As the clutches 40, 42, and 44, for example, a meshing clutch 48 shown in FIG. 2 is used. FIG. 2 is a main part configuration diagram schematically showing the configuration of the meshing clutch 48. As shown in FIG. 2, the meshing clutch 48 is disposed such that the driving side 48s and the driven side 48t are opposed to each other in the axial direction, and projecting clutch teeth 48p and 48q are intermittently provided on the sides facing each other. Is provided. Either one or both of the driven side 48t and the driving side 48s move in the axial direction and come in contact with and away from each other.

例えば、不図示のアクチュエータにより、矢印４８ｘで示すように被動側４８ｔが駆動側４８ｓの方向に付勢されて移動すると、図２（ａ）に示すように、駆動側４８ｓと被動側４８ｔのクラッチ歯４８ｐ，４８ｑが互いに間挿し合うように噛み合い、クラッチ４８はＯＮになる。   For example, when the driven side 48t is urged and moved in the direction of the driving side 48s as shown by an arrow 48x by an actuator (not shown), the clutch of the driving side 48s and the driven side 48t is shown in FIG. The teeth 48p and 48q mesh with each other so that the clutch 48 is turned on.

駆動側４８ｓと被動側４８ｔのクラッチ歯４８ｐ，４８ｑは、先端に斜面４８ｍ，４８ｎが形成されている。これにより、図２（ｂ）のように駆動側４８ｓと被動側４８ｔのクラッチ歯４８ｐ，４８ｑの位相がずれている状態であっても、駆動側４８ｓと被動側４８ｔとが位相が変わる方向に相対移動可能であれば、被動側４８ｔが駆動側４８ｓの方向に付勢されると位相が合い、クラッチ４８はＯＮになる。   The clutch teeth 48p and 48q on the driving side 48s and the driven side 48t have slopes 48m and 48n formed at the tips. Thus, even when the phases of the clutch teeth 48p and 48q of the driving side 48s and the driven side 48t are shifted as shown in FIG. 2B, the phase of the driving side 48s and the driven side 48t change in phase. If the relative movement is possible, the phase is matched when the driven side 48t is urged in the direction of the driving side 48s, and the clutch 48 is turned on.

すなわち、クラッチ４０，４２，４４には、位相が合う方向に駆動側４８ｓと被動側１８ｔが相対移動可能であれば、駆動側４８ｓと被動側４８ｔの位相がずれていてもＯＮにすることができる噛み合いクラッチ４８を用いる。   That is, if the driving side 48s and the driven side 18t are relatively movable in the phase matching direction, the clutches 40, 42, and 44 can be turned on even if the phases of the driving side 48s and the driven side 48t are shifted. A meshing clutch 48 that can be used is used.

図示していないが、クラッチ４０，４２，４４はアクチュエータによって駆動され、アクチュエータの動作は、制御装置によって制御される。また、非円形歯車対１８の位相は不図示のセンサにより検出され、検出信号は制御装置に入力される。制御装置は、回転を止めることなく減速比を切り替え、回転角度を正確に伝達し、かつ動力を効率的に伝達することができるように、クラッチ４０，４２，４４のＯＮ／ＯＦＦを制御する。   Although not shown, the clutches 40, 42 and 44 are driven by an actuator, and the operation of the actuator is controlled by a control device. The phase of the non-circular gear pair 18 is detected by a sensor (not shown), and the detection signal is input to the control device. The control device controls ON / OFF of the clutches 40, 42, and 44 so that the reduction ratio can be switched without stopping the rotation, the rotation angle can be accurately transmitted, and the power can be efficiently transmitted.

歯車対１６，１７及び非円形歯車対１８は、クラッチ４０，４２，４４のＯＮによって、入力軸１２と出力軸１４との間に選択的に連結される。クラッチ４０のＯＮにより第１の歯車対１６が入力軸１２と出力軸１４との間に連結されたとき、入力軸１２と出力軸１４との間の減速比は、相対的に大きい一定の減速比ＲＨとなる。クラッチ４２のＯＮにより第２の歯車対１７が入力軸１２と出力軸１４との間に連結されたとき、入力軸１２と出力軸１４との間の減速比は、相対的に小さい一定の減速比ＲＬとなる。クラッチ４４のＯＮにより非円形歯車対１８が入力軸１２と出力軸１４との間に連結されたとき、入力軸１２と出力軸１４との間の減速比は、少なくとも減速比ＲＨとＲＬとを含む範囲内で変化する。 The gear pair 16, 17 and the non-circular gear pair 18 are selectively connected between the input shaft 12 and the output shaft 14 by turning on the clutches 40, 42, 44. When the first gear pair 16 is connected between the input shaft 12 and the output shaft 14 by turning on the clutch 40, the reduction ratio between the input shaft 12 and the output shaft 14 is a relatively large constant deceleration. The ratio RH is obtained. When the second gear pair 17 is connected between the input shaft 12 and the output shaft 14 by turning on the clutch 42, the reduction ratio between the input shaft 12 and the output shaft 14 is a relatively small constant deceleration. The ratio RL . When the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14 by turning on the clutch 44, the reduction ratio between the input shaft 12 and the output shaft 14 is at least the reduction ratios RH and RL. It changes within the range including.

例えば図３に示すように、歯車対１６，１７及び非円形歯車対１８の歯車をかみ合いピッチ円（以下、単に「ピッチ円」という。）あるいはかみ合いピッチ曲線（以下、単に「ピッチ曲線」という。）で表し、歯面の図示を省略すると、第１及び第２の歯車対１６，１７は、対をなす歯車２０，３０；２２，３２のピッチ円２０ｐ，３０ｐ；２２ｐ，３２ｐが互いに接する円形歯車である。   For example, as shown in FIG. 3, the gear pairs 16, 17 and the non-circular gear pair 18 are meshed with a pitch circle (hereinafter simply referred to as “pitch circle”) or a mesh pitch curve (hereinafter simply referred to as “pitch curve”). When the tooth surfaces are not shown, the first and second gear pairs 16, 17 are circular in which the pitch circles 20p, 30p; 22p, 32p of the gears 20, 30; It is a gear.

非円形歯車対１８の対をなす歯車２４，３４は非円形歯車であり、非円形歯車対１８の対をなす歯車２４，３４のピッチ曲線２４ｐ，３４ｐは、減速比ＲＨの第１の歯車対１６のピッチ円２０ｐ，３０ｐの円弧と等しい第１の区間２５，３５と、減速比ＲＬの第２の歯車対のピッチ円２２ｐ，３２ｐの円弧と等しい第３の区間２７，３７と、減速比がＲＨとＲＬとの間で変化する第２及び第４の区間２６，３６；２８，３８とを有する。非円形歯車対１８の対をなす歯車２４，３４は、図３において矢印で示す方向に回転するとき、歯車２４，３４のピッチ曲線２４ｐ，３４ｐの各区間２５，３５；２６，３６；２７，３７；２８，３８同士が噛み合う。 The gears 24 and 34 forming the pair of the non-circular gear pair 18 are non-circular gears, and the pitch curves 24p and 34p of the gears 24 and 34 forming the pair of the non-circular gear pair 18 are the first gears having the reduction ratio RH . First sections 25 and 35 equal to the arcs of the pair 16 pitch circles 20p and 30p, and third sections 27 and 37 equal to the arcs of the pitch circles 22p and 32p of the second gear pair of the reduction gear ratio RL ; and a 28 and 38; reduction ratio and the second and fourth sections 26 and 36 which varies between R H and R L. When the gears 24 and 34 forming a pair of the non-circular gear pair 18 rotate in a direction indicated by an arrow in FIG. 3, the sections 25 and 35 of the pitch curves 24 p and 34 p of the gears 24 and 34; 37; 28, 38 mesh with each other.

非円形歯車対１８が入力軸１２と出力軸１４との間に連結されている状況において、非円形歯車対１８が、図３（ａ）に示すように、第３の区間２７，３７で噛み合う場合は、入力軸１２と出力軸１４との間の減速比はＲＬとなり、図３（ｂ）で示すように、第１の区間２５，３５で噛み合う場合は、入力軸１２と出力軸１４との間の減速比はＲＨとなる。第１の区間２５，３５と第３の区間２７，３７は、定速噛み合い区間である。 In a situation where the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14, the non-circular gear pair 18 meshes in the third sections 27 and 37 as shown in FIG. In this case, the reduction ratio between the input shaft 12 and the output shaft 14 is RL , and as shown in FIG. 3B, when meshing in the first sections 25 and 35, the input shaft 12 and the output shaft 14 The reduction ratio between and is RH . The first sections 25 and 35 and the third sections 27 and 37 are constant speed meshing sections.

第２の区間２６，３６、第４の区間２８，３８で噛み合う場合は、入力軸１２と出力軸１４との間の減速比は、ＲＬとＲＨの間で変化する。第２の区間２６，３６と第４の区間２８，３８は、変速噛み合い区間である。 When meshing in the second sections 26 and 36 and the fourth sections 28 and 38, the reduction ratio between the input shaft 12 and the output shaft 14 changes between RL and RH . The second sections 26 and 36 and the fourth sections 28 and 38 are shift meshing sections.

なお、非円形歯車対１８の一方の歯車が１回転すると他方の歯車が１回転して噛み合いが一巡する場合を例示したが、非円形歯車対は、一方の歯車が１回転すると他方の歯車が２回転以上回転して噛み合いが一巡する構成としてもよい。   In addition, although the case where one gear of the non-circular gear pair 18 makes one rotation and the other gear makes one rotation and the meshing makes a round, the non-circular gear pair shows that the other gear rotates when one gear makes one rotation. It is good also as a structure which rotates by 2 times or more and meshes | engages.

次に、変速機１０の動作について、図４及び図５を参照しながら説明する。図４（ａ）及び図５（ａ）は、非円形歯車対１８の減速比を模式的に示すグラフである。横軸は入力軸１２の回転角度、縦軸は入力側歯車２４と出力側歯車３４との間の減速比である。図４（ｂ）及び図５（ｂ）の表では、クラッチ４０，４２，４４のＯＮの状態を○印で示し、クラッチ４０，４２，４４のＯＦＦの状態は空欄としている。図４（ｂ）及び図５（ｂ）において、減速比ＲＨの第１の歯車対１６のクラッチ４０を「クラッチ（ＲＨ）」、減速比ＲＬの第２の歯車対１７のクラッチ４２を「クラッチ（ＲＬ）」、減速比が変化する非円形歯車対１８のクラッチ４４を「クラッチ（変速）」と表している。 Next, the operation of the transmission 10 will be described with reference to FIGS. 4 and 5. FIG. 4A and FIG. 5A are graphs schematically showing the reduction ratio of the non-circular gear pair 18. The horizontal axis represents the rotation angle of the input shaft 12, and the vertical axis represents the reduction ratio between the input side gear 24 and the output side gear 34. In the tables of FIG. 4 (b) and FIG. 5 (b), the ON state of the clutches 40, 42, 44 is indicated by ◯, and the OFF state of the clutches 40, 42, 44 is blank. In FIGS. 4 (b) and 4 FIG. 5 (b), the clutch 40 of the first gear pair 16 with the reduction ratio R H "clutch (R H)", the clutch 42 of the second gear pair 17 with the reduction ratio R L Is represented as “clutch (R L )”, and the clutch 44 of the non-circular gear pair 18 in which the reduction ratio changes is represented as “clutch (shift)”.

減速比ＲＨの第１の歯車対１６のクラッチ４０がＯＮ、クラッチ４２，４４がＯＦＦのときには、入力軸１２と出力軸１４との間は、一定の減速比ＲＨとなる。減速比ＲＬの第２の歯車対１７のクラッチ４２がＯＮ、クラッチ４０，４４がＯＦＦのときには、入力軸１２と出力軸１４との間は、一定の減速比ＲＬとなる。非円形歯車対１８の減速比は、図４（ａ）及び図５（ａ）に示すように、入力軸１２の回転に伴って減速比ＲＨとＲＬとを含む所定範囲内で変化する。なお、図４（ａ）及び図５（ａ）において、非円形歯車対１８の減速比が変化するときの曲線は模式的に図示されている。 When the clutch 40 of the first gear pair 16 having the reduction ratio RH is ON and the clutches 42, 44 are OFF, the reduction ratio RH is constant between the input shaft 12 and the output shaft 14. When the clutch 42 of the second gear pair 17 having the reduction ratio RL is ON and the clutches 40, 44 are OFF, the reduction ratio RL between the input shaft 12 and the output shaft 14 is constant. The reduction ratio of the non-circular gear pair 18 changes within a predetermined range including the reduction ratios RH and RL as the input shaft 12 rotates, as shown in FIGS. 4 (a) and 5 (a). . In FIGS. 4A and 5A, a curve when the reduction ratio of the non-circular gear pair 18 changes is schematically illustrated.

入力軸１２と出力軸１４との間の減速比をＲＨからＲＬに変える場合には、図４に示すようにクラッチ４０，４２，４４を動作させる。 When changing the reduction ratio between the input shaft 12 and the output shaft 14 from RH to RL , the clutches 40, 42, and 44 are operated as shown in FIG.

減速比ＲＨの第１の歯車対１６のクラッチ４０のみがＯＮであり、入力軸１２と出力軸１４との間の減速比がＲＨである状態で、非円形歯車対１８の減速比がＲＬからＲＨに変化する区間８１を通過した後、非円形歯車対１８の減速比が一定の減速比ＲＨとなる区間８２に入ったら、減速比ＲＨの第１の歯車対１６のクラッチ４０をＯＦＦにした後に、減速比が変化する非円形歯車対１８のクラッチ４４をＯＮにする。 Only the clutch 40 of the first gear pair 16 with the reduction ratio RH is ON, and the reduction ratio between the input shaft 12 and the output shaft 14 is RH , and the reduction ratio of the non-circular gear pair 18 is after passing through the section 81 changes from R L to R H, Once in section 82 which the reduction ratio of the non-circular gear pair 18 is constant reduction ratio R H, of the reduction ratio R H of the first gear pair 16 After the clutch 40 is turned off, the clutch 44 of the non-circular gear pair 18 whose speed reduction ratio changes is turned on.

すなわち、区間８２内において、最初の区間８２ａでは、減速比ＲＨの第１の歯車対１６のクラッチ４０はＯＮのままである。その次の区間８２ｘで、減速比ＲＨの第１の歯車対１６のクラッチ４０がＯＦＦになる。この区間８２ｘでは、すべてのクラッチ４０，４２，４４がＯＦＦである。さらに次の区間８２ｂで、減速比が変化する非円形歯車対１８のクラッチ４４がＯＮになる。 That is, in the section 82, in the first section 82a, the clutch 40 of the first gear pair 16 having the reduction ratio RH remains ON. In the next section 82x, the clutch 40 of the first gear pair 16 having the reduction ratio RH is turned off. In this section 82x, all the clutches 40, 42, 44 are OFF. Further, in the next section 82b, the clutch 44 of the non-circular gear pair 18 in which the speed reduction ratio changes is turned on.

次いで、非円形歯車対１８のクラッチ４４のみがＯＮの状態で、非円形歯車対１８の減速比がＲＨからＲＬに変化する区間８３を通過した後、非円形歯車対１８の減速比が一定の減速比ＲＬとなる区間８４に入ったら、減速比が変化する非円形歯車対１８のクラッチ４４をＯＦＦにした後に、減速比ＲＬの第２の歯車対１７のクラッチ４２をＯＮにして、減速比ＲＬの状態とする。 Next, in a state where only the clutch 44 of the non-circular gear pair 18 is ON, after passing through a section 83 where the reduction ratio of the non-circular gear pair 18 changes from RH to RL , the reduction ratio of the non-circular gear pair 18 is After entering the section 84 where the reduction ratio R L is constant, the clutch 44 of the non-circular gear pair 18 whose reduction ratio changes is turned OFF, and then the clutch 42 of the second gear pair 17 having the reduction ratio R L is turned ON. Thus, the speed reduction ratio RL is set.

すなわち、区間８４内において、最初の区間８４ａでは、減速比が変化する非円形歯車対１８のクラッチ４４はＯＮのままである。その次の区間８４ｘで、減速比が変化する非円形歯車対１８のクラッチ４４がＯＦＦになる。この区間８４ｘでは、すべてのクラッチ４０，４２，４４がＯＦＦである。さらに次の区間８４ｂで、減速比ＲＬの第２の歯車対１７のクラッチ４２がＯＮになり、入力軸１２と出力軸１４との間に第２の歯車対１７のみが連結され、入力軸１２と出力軸１４との間は一定の減速比ＲＬとなる。 That is, in the section 84, in the first section 84a, the clutch 44 of the non-circular gear pair 18 whose speed reduction ratio changes remains ON. In the next section 84x, the clutch 44 of the non-circular gear pair 18 whose speed reduction ratio changes is turned off. In this section 84x, all the clutches 40, 42, 44 are OFF. Further, in the next section 84b, the clutch 42 of the second gear pair 17 having the reduction ratio RL is turned on, and only the second gear pair 17 is connected between the input shaft 12 and the output shaft 14, and the input shaft 12 and the output shaft 14 have a constant reduction ratio RL .

入力軸１２と出力軸１４との間の減速比をＲＬからＲＨに変える場合には、図５に示すようにクラッチ４０，４２，４４を動作させる。 In order to change the reduction ratio between the input shaft 12 and the output shaft 14 from RL to RH , the clutches 40, 42, and 44 are operated as shown in FIG.

減速比ＲＬの第２の歯車対１７のクラッチ４２のみがＯＮであり、入力軸１２と出力軸１４との間の減速比がＲＬである状態で、非円形歯車対１８の減速比がＲＨからＲＬに変化する区間９１を通過した後、非円形歯車対１８の減速比が一定の減速比ＲＬとなる区間９２に入ったら、減速比ＲＬの第２の歯車対１７のクラッチ４２をＯＦＦにした後に、減速比が変化する非円形歯車対１８のクラッチ４４をＯＮにする。 Only the clutch 42 of the second gear pair 17 with the reduction ratio RL is ON, and the reduction ratio between the input shaft 12 and the output shaft 14 is RL , and the reduction ratio of the non-circular gear pair 18 is after passing through the section 91 changes from R H to R L, Once in section 92 which the reduction ratio of the non-circular gear pair 18 is constant reduction ratio R L, the speed reduction ratio R L of the second gear pair 17 After the clutch 42 is turned off, the clutch 44 of the non-circular gear pair 18 whose speed reduction ratio changes is turned on.

すなわち、区間９２内において、最初の区間９２ａでは、減速比ＲＬの第２の歯車対１７のクラッチ４２はＯＮのままである。その次の区間９２ｘで、減速比ＲＬの第２の歯車対１７のクラッチ４２がＯＦＦになる。この区間９２ｘでは、すべてのクラッチ４０，４２，４４がＯＦＦである。さらに次の区間９２ｂで、減速比が変化する非円形歯車対１８のクラッチ４４がＯＮになる。 That is, in the section 92, in the first section 92a, the clutch 42 of the second gear pair 17 having the reduction ratio RL remains ON. In the next section 92x, the clutch 42 of the second gear pair 17 having the reduction ratio RL is turned off. In this section 92x, all the clutches 40, 42, 44 are OFF. Further, in the next section 92b, the clutch 44 of the non-circular gear pair 18 in which the speed reduction ratio changes is turned on.

次いで、非円形歯車対１８のクラッチ４４のみがＯＮの状態で、非円形歯車対１８の減速比がＲＬからＲＨに変化する区間９３を通過した後、非円形歯車対１８の減速比が一定の減速比ＲＨとなる区間９４に入ったら、減速比が変化する非円形歯車対１８のクラッチ４４をＯＦＦにした後に、減速比ＲＨの第１の歯車対１６のクラッチ４０をＯＮにして、減速比ＲＨの状態とする。 Next, after passing through the section 93 where the reduction ratio of the non-circular gear pair 18 changes from RL to RH with only the clutch 44 of the non-circular gear pair 18 being ON, the reduction ratio of the non-circular gear pair 18 is When entering a section 94 where the reduction ratio RH is constant, the clutch 44 of the non-circular gear pair 18 whose speed reduction ratio changes is turned OFF, and then the clutch 40 of the first gear pair 16 having the reduction ratio RH is turned ON. Thus, the speed reduction ratio RH is set.

すなわち、区間９４内において、最初の区間９４ａでは、減速比が変化する非円形歯車対１８のクラッチ４４はＯＮのままである。その次の区間９４ｘで、減速比が変化する非円形歯車対１８のクラッチ４４がＯＦＦになる。この区間９４ｘでは、すべてのクラッチ４０，４２，４４がＯＦＦである。さらに次の区間９４ｂで、減速比ＲＨの第１の歯車対１６のクラッチ４０がＯＮになり、入力軸１２と出力軸１４との間に第１の歯車対１６のみが連結され、入力軸１２と出力軸１４との間は一定の減速比ＲＨになる。 That is, in the section 94, in the first section 94a, the clutch 44 of the non-circular gear pair 18 whose speed reduction ratio changes remains ON. In the next section 94x, the clutch 44 of the non-circular gear pair 18 whose speed reduction ratio changes is turned off. In this section 94x, all the clutches 40, 42, 44 are OFF. Further, in the next section 94b, the clutch 40 of the first gear pair 16 having the reduction ratio RH is turned ON, and only the first gear pair 16 is connected between the input shaft 12 and the output shaft 14, and the input shaft 12 and the output shaft 14 have a constant reduction ratio RH .

以上のように入力軸１２と出力軸１４との間の減速比をＲＨからＲＬに、あるいはＲＬからＲＨに変える場合、クラッチを切り替える区間８２，８４，９２，９４においてＯＮ／ＯＦＦを切り替える２つのクラッチのうち一方のクラッチ４０，４４，４２，４４をＯＮからＯＦＦにした後に、他方のクラッチ４４，４２，４４，４０をＯＮにしており、２つのクラッチは同時にＯＮにしない。区間８２，８４，９２，９４においてＯＮ／ＯＦＦを切り替える２つのクラッチのうち、後でＯＮとなる他方のクラッチ４４，４２，４４，４０は、位相が合う方向に駆動側と被動側が相対移動可能であれば駆動側と被動側の位相がずれていてもＯＮにすることができる噛み合いクラッチであるため、駆動側と被動側の位相を一致させる必要がない。このため、クラッチ４０，４２，４４や歯車２０，２２，２４，３０，３２，３４の設計の自由度を高くでき、最適な性能となるクラッチ４０，４２，４４や歯車２０，２２，２４，３０，３２，３４を備えた変速機１０を実現しやすい。 When changing the reduction ratio between the input shaft 12 and the output shaft 14 as described above from R H to R L, or from R L to R H, ON / OFF in a section 82,84,92,94 switching the clutch After switching one clutch 40, 44, 42, 44 from ON to OFF, the other clutch 44, 42, 44, 40 is turned ON, and the two clutches are not turned ON at the same time. Of the two clutches that are switched ON / OFF in the sections 82, 84, 92, and 94, the other clutch 44, 42, 44, and 40 that is turned ON later can be moved relative to each other in the direction in which the phases match. If this is a meshing clutch that can be turned on even if the driving side and the driven side are out of phase, it is not necessary to match the phases of the driving side and the driven side. Therefore, the degree of freedom in designing the clutches 40, 42, 44 and the gears 20, 22, 24, 30, 32, 34 can be increased, and the clutches 40, 42, 44 and the gears 20, 22, 24, It is easy to realize the transmission 10 including 30, 32, and 34.

クラッチ４０，４２，４４は、区間８２，８４，９２，９４において駆動側と被動側とが同じ速度のときに、すなわち相対速度がゼロのときに、ＯＮ／ＯＦＦの切り替えを行う。このため、通常の歯車式変速機で用いられるシンクロコーン（相対速度をゼロにするための摩擦部材）は不要である。   The clutches 40, 42, and 44 perform ON / OFF switching when the driving side and the driven side have the same speed in the sections 82, 84, 92, and 94, that is, when the relative speed is zero. For this reason, the synchro cone (friction member for making a relative speed zero) used with a normal gear type transmission is unnecessary.

なお、すべてのクラッチ４０，４２，４４がＯＦＦになる区間８２ｘ，８４ｘでは、駆動力が伝達されないので、この区間８２ｘ，８４ｘの時間は、できるだけ短くすることが好ましい。   In the sections 82x and 84x in which all the clutches 40, 42, and 44 are turned off, the driving force is not transmitted. Therefore, it is preferable that the times of the sections 82x and 84x be as short as possible.

次に、変速機１０の具体的な構成例について、図６〜図８を参照しながら説明する。   Next, a specific configuration example of the transmission 10 will be described with reference to FIGS.

図６の断面図に示すように、入力軸１２に、歯車対１６，１７及び非円形歯車対１８の入力側歯車２０，２２，２４が順に固定されている。出力軸１４には、歯車対１６，１７及び非円形歯車対１８の出力側歯車３０，３２，３４が相対回転可能かつ、軸方向移動不可能な状態で順に支持されている。第１の歯車対１６の出力側歯車３０と第２の歯車対１７の出力側歯車３２との間には、クラッチ５００のシフター４１が配置されている。クラッチ５００は、シフター４１を兼用することで、第１の歯車対１６用のクラッチ４０と第２の歯車対１７用のクラッチ４２との両方の機能を実現している。第２の歯車対１７の出力側歯車３２と非円形歯車対１８の出力側歯車３４との間には、非円形歯車対用クラッチ５０２のシフター４５が配置されている。クラッチ５００，５０２のシフター４１，４５は、出力軸１４に形成されたスプライン溝に摺動自在に支持されており、出力軸１４に沿って軸方向には移動自在であるが、出力軸１４に対する相対回転はできない状態であり、出力軸１４と一体となって回転するようになっている。   As shown in the sectional view of FIG. 6, the input side gears 20, 22, 24 of the gear pair 16, 17 and the non-circular gear pair 18 are fixed to the input shaft 12 in order. On the output shaft 14, the output side gears 30, 32, 34 of the gear pair 16, 17 and the non-circular gear pair 18 are sequentially supported in a state in which they can be relatively rotated and cannot be moved in the axial direction. A shifter 41 of the clutch 500 is disposed between the output side gear 30 of the first gear pair 16 and the output side gear 32 of the second gear pair 17. The clutch 500 also serves as the shifter 41 to realize both functions of the clutch 40 for the first gear pair 16 and the clutch 42 for the second gear pair 17. A shifter 45 of the non-circular gear pair clutch 502 is disposed between the output side gear 32 of the second gear pair 17 and the output side gear 34 of the non-circular gear pair 18. The shifters 41 and 45 of the clutches 500 and 502 are slidably supported in spline grooves formed on the output shaft 14 and are movable in the axial direction along the output shaft 14. The relative rotation is impossible, and the output shaft 14 is rotated integrally.

クラッチ５００，５０２のシフター４１，４５の外周面には、不図示のアクチュエータが嵌合する溝４１ｘ、４５ｘが形成されている。クラッチ５００のシフター４１は、溝４１ｘに嵌合する不図示のアクチュエータの駆動によって、図６に示した中間位置から、矢印４１ｓ，４１ｔに示すように両側に移動する。非円形歯車対用クラッチ５０２のシフター４５は、溝４５ｘに嵌合する不図示のアクチュエータの駆動によって、図５に示した待機位置から、矢印４５ｔで示す片側だけに移動する。   Grooves 41x and 45x into which actuators (not shown) are fitted are formed on the outer peripheral surfaces of the shifters 41 and 45 of the clutches 500 and 502. The shifter 41 of the clutch 500 moves from the intermediate position shown in FIG. 6 to both sides as indicated by arrows 41 s and 41 t by driving an actuator (not shown) fitted in the groove 41 x. The shifter 45 of the non-circular gear pair clutch 502 moves from the standby position shown in FIG. 5 to only one side indicated by an arrow 45t by driving an actuator (not shown) fitted in the groove 45x.

クラッチ５００のシフター４１は、第１の歯車対１６の出力側歯車３０に対向する側面と、第２の歯車対１７の出力側歯車３２に対向する側面に、所定のピッチで突起（ドグ）４１ａ，４１ｂが形成されている。第１の歯車対１６の出力側歯車３０と第２の歯車対１７の出力側歯車３２には、クラッチ５００の構成要素として、クラッチ５００のシフター４１に対向する側面に、クラッチ５００のシフター４１の突起４１ａ，４１ｂに対応して、所定のピッチで凹部（ドグ穴）３１，３３が形成されている。矢印４１ｓ，４１ｔで示す方向にクラッチ５００のシフター４１が移動したとき、クラッチ５００のシフター４１の突起４１ａ，４１ｂが、出力側歯車３０，３２の凹部３１，３３に嵌合し、クラッチ５００のシフター４１を介して出力軸１４と出力側歯車３０，３２とが一体となって回転する。すなわち、入力軸１２と出力軸１４との間に第１又は第２の歯車対１６，１７が連結され、入力軸１２から、第１又は第２の歯車対１６，１７を介して出力軸１４に、回転角度を正確に伝達し、かつ動力を効率的に伝達することができる。   The shifter 41 of the clutch 500 has protrusions (dogs) 41a at a predetermined pitch on the side surface of the first gear pair 16 facing the output side gear 30 and the side surface of the second gear pair 17 facing the output side gear 32. , 41b are formed. The output side gear 30 of the first gear pair 16 and the output side gear 32 of the second gear pair 17 are provided as components of the clutch 500 on the side surface of the clutch 500 that faces the shifter 41 of the clutch 500. Corresponding to the protrusions 41a and 41b, recesses (dog holes) 31 and 33 are formed at a predetermined pitch. When the shifter 41 of the clutch 500 moves in the direction indicated by the arrows 41 s and 41 t, the protrusions 41 a and 41 b of the shifter 41 of the clutch 500 are fitted into the recesses 31 and 33 of the output side gears 30 and 32, and the shifter of the clutch 500 is moved. The output shaft 14 and the output side gears 30 and 32 are rotated together via 41. That is, the first or second gear pair 16, 17 is connected between the input shaft 12 and the output shaft 14, and the output shaft 14 is connected from the input shaft 12 via the first or second gear pair 16, 17. In addition, the rotation angle can be accurately transmitted and power can be transmitted efficiently.

非円形歯車対用クラッチ５０２のシフター４５は、非円形歯車対１８の出力側歯車３４に対向する側面に、所定のピッチで突起（ドグ）４５ｂが形成されている。非円形歯車対１８の出力側歯車３４には、非円形歯車対用クラッチ５０２の構成要素として、非円形歯車対用クラッチ５０２のシフター４５に対向する側面に、非円形歯車対用クラッチ５０２のシフター４５の突起４５ｂに対応して、所定のピッチで凹部（ドグ穴）３５が形成されており、矢印４５ｔで示す方向に非円形歯車対用クラッチ５０２のシフター４５が移動したとき、非円形歯車対用クラッチ５０２のシフター４５の突起４５ｂが、非円形歯車対１８の出力側歯車３４の凹部３５に嵌合し、非円形歯車対用クラッチ５０２のシフター４５を介して出力軸１４と出力側歯車３４とが一体となって回転する。すなわち、入力軸１２と出力軸１４との間に非円形歯車対１８が連結され、入力軸１２から、非円形歯車対１８を介して出力軸１４に、回転角度を正確に伝達し、かつ動力を効率的に伝達することができる。   The shifter 45 of the non-circular gear pair clutch 502 has protrusions (dogs) 45 b formed at a predetermined pitch on the side surface of the non-circular gear pair 18 that faces the output side gear 34. The output side gear 34 of the non-circular gear pair 18 includes, as a component of the non-circular gear pair clutch 502, a shifter of the non-circular gear pair clutch 502 on a side surface facing the shifter 45 of the non-circular gear pair clutch 502. Recesses (dog holes) 35 are formed at a predetermined pitch corresponding to the protrusions 45b of 45, and when the shifter 45 of the non-circular gear pair clutch 502 moves in the direction indicated by the arrow 45t, the non-circular gear pair The protrusion 45 b of the shifter 45 of the clutch for clutch 502 fits into the recess 35 of the output side gear 34 of the non-circular gear pair 18, and the output shaft 14 and the output side gear 34 via the shifter 45 of the non-circular gear pair clutch 502. And rotate together. That is, the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14, and the rotational angle is accurately transmitted from the input shaft 12 to the output shaft 14 via the non-circular gear pair 18, and the power Can be transmitted efficiently.

次に、この変速機１０の動作の一例について、図７及び図８を参照しながら説明する。   Next, an example of the operation of the transmission 10 will be described with reference to FIGS.

図７（ａ）に示すように、クラッチ５００のシフター４１が矢印４１ｓで示す方向に移動して第１の歯車対１６の出力側歯車３０に嵌合し、非円形歯車対用クラッチ５０２のシフター４５が待機位置にあるとき、入力軸１２と出力軸１４との間には、第１の歯車対１６のみが連結される。このとき、回転角度及び動力は、図７（ａ）において破線で示すように、入力軸１２から第１の歯車対１６の入力側歯車２０、出力側歯車３０、クラッチ５００のシフター４１を介して、出力軸１４に伝達され、減速比はＲＨとなる。 As shown in FIG. 7A, the shifter 41 of the clutch 500 moves in the direction indicated by the arrow 41 s and engages with the output side gear 30 of the first gear pair 16, so that the shifter of the non-circular gear pair clutch 502. When 45 is in the standby position, only the first gear pair 16 is connected between the input shaft 12 and the output shaft 14. At this time, the rotation angle and power are changed from the input shaft 12 through the input gear 20 of the first gear pair 16, the output gear 30, and the shifter 41 of the clutch 500, as indicated by broken lines in FIG. Is transmitted to the output shaft 14, and the reduction ratio becomes RH .

減速比をＲＨからＲＬに切り替える場合には、非円形歯車対１８の減速比がＲＨになる状態の間に、図７（ｂ）に示すように、クラッチ５００のシフター４１が中間位置に移動し、第１の歯車対１６の出力側歯車３０との嵌合が解除される。 When the reduction ratio is switched from RH to RL , the shifter 41 of the clutch 500 is in an intermediate position as shown in FIG. 7B while the reduction ratio of the non-circular gear pair 18 is RH . And the fitting of the first gear pair 16 with the output side gear 30 is released.

次いで、非円形歯車対１８の減速比がＲＨになる状態の間に、図７（ｃ）に示すように、非円形歯車対用クラッチ５０２のシフター４５が矢印４５ｔで示す方向に移動して非円形歯車対１８の出力側歯車３４に嵌合し、入力軸１２と出力軸１４との間に、非円形歯車対１８が連結される。これにより、回転角度及び動力は、破線で示すように、入力軸１２から、非円形歯車対１８の入力側歯車２４、出力側歯車３４、非円形歯車対用クラッチ５０２のシフター４５を介して、出力軸１４に伝達される。 Next, while the reduction ratio of the non-circular gear pair 18 is RH , the shifter 45 of the non-circular gear pair clutch 502 moves in the direction indicated by the arrow 45t as shown in FIG. 7C. The output side gear 34 of the non-circular gear pair 18 is fitted, and the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14. As a result, as shown by the broken line, the rotation angle and power are transmitted from the input shaft 12 via the input side gear 24 of the non-circular gear pair 18, the output side gear 34, and the shifter 45 of the non-circular gear pair clutch 502. It is transmitted to the output shaft 14.

次いで、非円形歯車対１８のみが連結された状態で、非円形歯車対１８の減速比がＲＨからＲＬに変化する。 Next, with only the non-circular gear pair 18 connected, the reduction ratio of the non-circular gear pair 18 changes from RH to RL .

次いで、非円形歯車対１８の減速比がＲＬになると、図８（ｄ）に示すように、非円形歯車対用クラッチ５０２のシフター４５が待機位置に移動し、非円形歯車対１８の出力側歯車３４との嵌合が解除される。 Next, when the reduction ratio of the non-circular gear pair 18 reaches RL , the shifter 45 of the non-circular gear pair clutch 502 moves to the standby position as shown in FIG. The fitting with the side gear 34 is released.

次いで、図８（ｅ）に示すように、クラッチ５００のシフター４１が矢印４１ｔで示す方向に移動して第２の歯車対１７の出力側歯車３２に嵌合し、入力軸１２と出力軸１４との間に、第２の歯車対１７が連結される。これにより、回転角度及び動力は、破線で示すように、入力軸１２から、第２の歯車対１７の入力側歯車２２、出力側歯車３２、クラッチ５００のシフター４１を介して、出力軸１４に伝達され、一定の減速比ＲＬとなり、減速比の切り替えが完了する。 Next, as shown in FIG. 8 (e), the shifter 41 of the clutch 500 moves in the direction indicated by the arrow 41t and engages with the output side gear 32 of the second gear pair 17, and the input shaft 12 and the output shaft 14 Between the second gear pair 17 and the second gear pair 17. As a result, the rotation angle and power are transferred from the input shaft 12 to the output shaft 14 via the input gear 22 of the second gear pair 17, the output gear 32, and the shifter 41 of the clutch 500, as indicated by the broken line. This is transmitted to a constant reduction ratio RL , and the reduction ratio switching is completed.

＜実施例２＞ 実施例２で用いる変速機１０ａについて、図９を参照しながら説明する。   <Embodiment 2> A transmission 10a used in Embodiment 2 will be described with reference to FIG.

実施例２の変速機１０ａは、実施例１の変速機１０と略同様に構成されている。以下では、実施例１との相違点を中心に説明し、同じ構成部分には同じ符号を用いる。   The transmission 10a of the second embodiment is configured in substantially the same manner as the transmission 10 of the first embodiment. Below, it demonstrates centering around difference with Example 1, and uses the same code | symbol for the same component.

図９は、実施例２の変速機１０ａの構成を模式的に示す機構図である。図９に示すように、実施例２の変速機１０ａは、実施例１と異なり、増減速装置２９，３９を備える。入力軸１２ａ及び出力軸１４ａは、第１及び第２の歯車対１６，１７が配置される第１部分１２ｓ，１４ｓと、非円形歯車対１８が配置される第２部分１２ｔ，１４ｔとに分割されている。入力軸１２ａの第１部分１２ｓと入力軸１２ａの第２部分１２ｔとは、第１の増減速装置２９を介して回転伝達可能に結合されている。出力軸１４ａの第１部分１４ｓと出力軸１４ａの第２部分１４ｔとは、第２の増減速装置３９を介して回転伝達可能に結合されている。   FIG. 9 is a mechanism diagram schematically showing the configuration of the transmission 10a of the second embodiment. As shown in FIG. 9, the transmission 10 a according to the second embodiment includes the speed increasing / decelerating devices 29 and 39, unlike the first embodiment. The input shaft 12a and the output shaft 14a are divided into first portions 12s and 14s where the first and second gear pairs 16 and 17 are disposed, and second portions 12t and 14t where the non-circular gear pair 18 is disposed. Has been. The first portion 12 s of the input shaft 12 a and the second portion 12 t of the input shaft 12 a are coupled via a first speed increasing / decreasing device 29 so as to be able to transmit rotation. The first portion 14s of the output shaft 14a and the second portion 14t of the output shaft 14a are coupled via a second speed increasing / decreasing device 39 so as to be able to transmit rotation.

ここで、第１の増減速装置２９の減速比を、入力軸１２ａの第１部分１２ｓの回転速度Ｎｉ１と入力軸１２ａの第２部分１２ｔの回転速度Ｎｉ２とを用いて、Ｎｉ１／Ｎｉ２と定義する。第２の増減速装置３９の減速比を、出力軸１４ａの第２部分１４ｔの回転速度Ｎｏ２と出力軸１４ａの第１部分１４ｓの回転速度Ｎｏ１を用いて、Ｎｏ２／Ｎｏ１と定義する。第２の増減速装置３９の減速比の定義は、Ｎｏ１／Ｎｏ２ではないことに留意する必要がある。 Here, the reduction ratio of the first speed increasing / decreasing device 29 is determined by using the rotational speed N i1 of the first portion 12 s of the input shaft 12 a and the rotational speed N i2 of the second portion 12 t of the input shaft 12 a using N i1 / N i2 is defined. The speed reduction ratio of the second speed increasing / decreasing device 39 is defined as N o2 / N o1 using the rotation speed N o2 of the second portion 14 t of the output shaft 14 a and the rotation speed N o1 of the first portion 14 s of the output shaft 14 a. To do. It should be noted that the definition of the reduction ratio of the second speed increasing / decreasing device 39 is not N o1 / N o2 .

例えば、増減速装置２９，３９により、非円形歯車対１８側の回転速度を遅くすることができる。すなわち、入力軸１２ａの第１部分１２ｓと第２部分１２ｔの間に設けられた第１の増減速装置２９の減速比をＲ０とし、入力軸１２ａの第１部分１２ｓの回転速度に対して、入力軸１２ａの第２部分１２ｔの回転速度を遅くするとともに、出力軸１４ａの第２部分１４ｔと第１部分１４ｓとの間に設けられた第２の増減速装置３９の減速比を１／Ｒ０とし、出力軸１４ａの第１部分１４ｓの回転速度に対して、出力軸１４ａの第２部分１４ｔの回転速度を遅くすることで、非円形歯車対１８側の回転速度を遅くする。これによって、入力軸１２ａの第１部分１２ｓの回転が高速であっても、実施例１と同様に、非円形歯車対１８側の噛み合いによって減速比を変化させながら回転を伝達することができる。 For example, the rotational speeds on the non-circular gear pair 18 side can be reduced by the speed increasing / decreasing devices 29 and 39. That is, the reduction ratio of the first speed increasing / decreasing device 29 provided between the first portion 12s and the second portion 12t of the input shaft 12a is R0, and the rotational speed of the first portion 12s of the input shaft 12a is The rotational speed of the second portion 12t of the input shaft 12a is decreased, and the reduction ratio of the second speed increasing / decreasing device 39 provided between the second portion 14t and the first portion 14s of the output shaft 14a is reduced to 1 /. By setting R0 , the rotational speed of the second portion 14t of the output shaft 14a is made slower than the rotational speed of the first portion 14s of the output shaft 14a, so that the rotational speed on the non-circular gear pair 18 side is slowed. Thus, even when the rotation of the first portion 12s of the input shaft 12a is high speed, the rotation can be transmitted while changing the reduction ratio by the meshing on the non-circular gear pair 18 side as in the first embodiment.

なお、増減速装置２９，３９に同じ構成の増減速装置を用い、入力側と出力側を入れ替えて、一方で減速し、他方で増速してもよい。   In addition, the speed increasing / decreasing device having the same configuration may be used for the speed increasing / decreasing devices 29, 39, and the input side and the output side may be interchanged to decelerate one side and increase the speed on the other side.

増減速装置２９，３９により、非円形歯車対１８側の回転速度を速くすることも可能である。   It is also possible to increase the rotational speed on the non-circular gear pair 18 side by the speed increasing / decreasing devices 29 and 39.

変速機１０ａの減速比は、増減速装置２９，３９と非円形歯車対１８とによって全体として切り換えればよいので、入力軸１２ａ側に設ける第１の増減速装置２９の減速比Ｒｉｎと、出力軸１４ａ側に設ける第２の増減速装置３９の減速比Ｒｏｕｔとが、Ｒｉｎ×Ｒｏｕｔ＝１とならなくても構わない。 Since the speed reduction ratio of the transmission 10a may be switched as a whole by the speed increasing / decreasing devices 29, 39 and the non-circular gear pair 18, the speed reducing ratio R in of the first speed increasing / decreasing device 29 provided on the input shaft 12a side, The reduction ratio R out of the second speed increasing / decreasing device 39 provided on the output shaft 14a side may not be R in × R out = 1.

例えば、第１の歯車対１６の減速比がＲ１、第２の歯車対１７の減速比がＲ２、非円形歯車対１８のある区間の減速比がＲ１'、非円形歯車対１８の他の区間の減速比がＲ２'とすると、次の２つの式、
Ｒ１＝Ｒｉｎ×Ｒ１'×Ｒｏｕｔ （１）
Ｒ２＝Ｒｉｎ×Ｒ２'×Ｒｏｕｔ （２）
を満たせば、変速機１０ａの減速比を、Ｒ１からＲ２、又はＲ２からＲ１に切り換えることができる。 For example, the reduction ratio of the first gear pair 16 is R1, the reduction ratio of the second gear pair 17 is R2, the reduction ratio of one section of the non-circular gear pair 18 is R1 ', and the other section of the non-circular gear pair 18 If the reduction ratio of R2 ′ is
R1 = R in × R1 ′ × R out (1)
R2 = Rin * R2 '* Rout (2)
If satisfied, the reduction ratio of the transmission 10a can be switched from R1 to R2 or from R2 to R1.

実施例１の変速機１０では、入力が高速回転であると、クラッチの切り換え動作をすべき時間が短くなり、減速比の切り換えが困難になる場合がある。   In the transmission 10 according to the first embodiment, when the input is high-speed rotation, the time required for the clutch switching operation is shortened, and switching of the reduction ratio may be difficult.

これに対し、実施例２の変速機１０ａは、入力が高速回転であっても、適宜な減速比の増減速装置２９，３９により非円形歯車対１８の回転を遅くすることで、クラッチの切り換え動作をすべき時間を長くすることができるので、容易に減速比を変えることができる。   On the other hand, in the transmission 10a of the second embodiment, even when the input is high-speed rotation, the rotation of the non-circular gear pair 18 is slowed down by the speed increasing / decreasing devices 29 and 39 having an appropriate reduction ratio, thereby switching the clutch. Since the time for the operation can be increased, the reduction ratio can be easily changed.

逆に、入力が低速回転である場合には、適宜な減速比の増減速装置２９，３９により非円形歯車対１８の回転を速くすることで、減速比の切り換えに要する時間を短縮することができる。   On the other hand, when the input is a low-speed rotation, the speed required for switching the reduction ratio can be shortened by increasing the rotation of the non-circular gear pair 18 with the speed increasing / decreasing devices 29 and 39 having an appropriate reduction ratio. it can.

また、非円形歯車対１８の設計の自由度を高くすることも可能である。   Further, the degree of freedom in designing the non-circular gear pair 18 can be increased.

非円形歯車対用クラッチは、第１の増減速装置２９と入力軸１２ａの第２部分１２ｔと非円形歯車対１８と出力軸１４ａの第２部分１４ｔと第２の増減速装置３９とを介して入力軸１２ａの第１部分１２ｓと出力軸１４ａの第１部分１４ｓとの間を解除可能に連結すればよい。そのため、例えば、非円形歯車対用クラッチは、入力軸１２ａの第１部分１２ｓと第１の増減速装置２９との間、第１の増減速装置２９と入力軸１２ａの第２部分１２ｔとの間、出力軸１４ａの第２部分１４ｔと第２の増減速装置３９との間、又は第２の増減速装置３９と出力軸１４ａの第１部分１４ｓとの間に設けることもできる。この場合、非円形歯車対１８が常に入力軸１２ａの第２部分１２ｔと出力軸１４ａの第２部分１４ｔとの間に連結された構成にすることができる。   The clutch for the non-circular gear pair includes the first speed increasing / decreasing device 29, the second portion 12t of the input shaft 12a, the non-circular gear pair 18, the second portion 14t of the output shaft 14a, and the second speed increasing / decreasing device 39. The first portion 12s of the input shaft 12a and the first portion 14s of the output shaft 14a may be releasably connected. Therefore, for example, the non-circular gear pair clutch is provided between the first portion 12s of the input shaft 12a and the first speed increasing / decreasing device 29, and between the first speed increasing / decreasing device 29 and the second portion 12t of the input shaft 12a. It can also be provided between the second portion 14t of the output shaft 14a and the second speed increasing / decreasing device 39, or between the second speed increasing / decreasing device 39 and the first portion 14s of the output shaft 14a. In this case, the non-circular gear pair 18 can always be connected between the second portion 12t of the input shaft 12a and the second portion 14t of the output shaft 14a.

実施例２の変速機１０ａは、実施例１と同じ変速方法で、減速比をＲＨからＲＬに変えたり、ＲＬからＲＨに変えたりすることができる。実施例１と同じく、クラッチ４０，４２，４４は、位相が合う方向に駆動側と被動側が相対移動可能であれば駆動側と被動側の位相がずれていてもＯＮにすることができる噛み合いクラッチであるため、駆動側と被動側の位相を一致させる必要がない。このため、クラッチ４０，４２，４４や歯車２０，２２，２４，３０，３２，３４の設計の自由度を高くでき、最適な性能となるクラッチ４０，４２，４４や歯車２０，２２，２４，３０，３２，３４を備えた変速機１０ａを実現しやすい。 Transmission 10a of Example 2, the same transmission method as that of Example 1, the reduction ratio changing from R H to R L, may be changing from R L to R H. As in the first embodiment, the clutches 40, 42, 44 are meshing clutches that can be turned on even if the driving side and the driven side are out of phase as long as the driving side and the driven side can be moved relative to each other in the phase matching direction. Therefore, it is not necessary to match the phases of the driving side and the driven side. Therefore, the degree of freedom in designing the clutches 40, 42, 44 and the gears 20, 22, 24, 30, 32, 34 can be increased, and the clutches 40, 42, 44 and the gears 20, 22, 24, It is easy to realize the transmission 10a including 30, 32, and 34.

＜まとめ＞ 以上に説明した非円形歯車対を用いた変速機の変速方法は、クラッチや歯車の設計の自由度を高くでき、最適な性能となるクラッチや歯車を備えた変速機を実現しやすい。   <Summary> The speed change method of the transmission using the non-circular gear pair described above can increase the degree of freedom in designing the clutch and the gear, and can easily realize the transmission including the clutch and the gear with the optimum performance. .

なお、本発明は、上記実施の形態に限定されるものではなく、種々変更を加えて実施することが可能である。   The present invention is not limited to the above embodiment, and can be implemented with various modifications.

例えば、本発明は、変速機のクラッチ及び非円形歯車対用クラッチの少なくとも一つが噛み合いクラッチであればよく、噛み合いクラッチ以外の滑りクラッチなどのクラッチを含んでいても構わない。   For example, in the present invention, at least one of the clutch of the transmission and the clutch for the non-circular gear pair may be a meshing clutch, and may include a clutch such as a slipping clutch other than the meshing clutch.

また、３つ以上の歯車対を備えたり、２つ以上の非円形歯車対を備えたりしてもよい。歯車対及び非円形歯車対の軸方向の配置順序は任意に選択できる。クラッチ及び非円形歯車対用クラッチは、入力軸側に設けてもよい。   Also, three or more gear pairs may be provided, or two or more non-circular gear pairs may be provided. The arrangement order of the gear pairs and the non-circular gear pairs in the axial direction can be arbitrarily selected. The clutch and the clutch for the non-circular gear pair may be provided on the input shaft side.

１０，１０ａ 変速機
１２，１２ａ 入力軸（入力部材）
１２ｓ 第１部分（入力部材の第１部分）
１２ｔ 第２部分（入力部材の第２部分）
１４，１４ａ 出力軸（出力部材）
１４ｓ 第１部分（出力部材の第１部分）
１４ｔ 第２部分（出力部材の第２部分）
１６，１７ 歯車対
１８ 非円形歯車対
２０，２２，２４ 歯車（入力側歯車）
２５ 第１の区間（定速噛み合い区間）
２６ 第２の区間（変速噛み合い区間）
２７ 第３の区間（定速噛み合い区間）
２８ 第４の区間（変速噛み合い区間）
２９ 増減速装置（第１の増減速装置）
３０，３２，３４ 歯車（出力側歯車）
３５ 第１の区間（定速噛み合い区間）
３６ 第２の区間（変速噛み合い区間）
３７ 第３の区間（定速噛み合い区間）
３８ 第４の区間（変速噛み合い区間）
３９ 増減速装置（第２の増減速装置）
４０，４２ クラッチ
４４ 非円形歯車対用クラッチ
４８ 噛み合いクラッチ 10, 10a Transmission 12, 12a Input shaft (input member)
12s first part (first part of input member)
12t second part (second part of input member)
14, 14a Output shaft (output member)
14s first part (first part of output member)
14t second part (second part of output member)
16, 17 Gear pair 18 Non-circular gear pair 20, 22, 24 Gear (input side gear)
25 1st section (constant speed meshing section)
26 Second section (shift meshing section)
27 3rd section (constant speed meshing section)
28 4th section (shift meshing section)
29 Speed increase / decrease device (first speed increase / decrease device)
30, 32, 34 gear (output side gear)
35 First section (constant speed meshing section)
36 Second section (shift meshing section)
37 3rd section (constant speed meshing section)
38 4th section (shift meshing section)
39 Speed increase / decrease device (second speed increase / decrease device)
40, 42 Clutch 44 Non-circular gear pair clutch 48 Meshing clutch

Claims (4)

回転可能に支持された入力部材と、
回転可能に支持された出力部材と、
前記入力部材と前記出力部材との間にそれぞれ配置され、前記入力部材と前記出力部材との間に連結されたときの減速比が一定である、少なくとも２つの歯車対と、
前記入力部材と前記出力部材との間に、少なくとも２つの前記歯車対を、それぞれ、ＯＮのときに連結し、ＯＦＦのときに連結を解除する、少なくとも２つクラッチと、
前記入力部材と前記出力部材との間に配置され、前記入力部材と前記出力部材との間に連結されたときの減速比が変動する、少なくとも１つの非円形歯車対と、
前記入力部材と前記出力部材との間に前記非円形歯車対を、ＯＮのときに連結し、ＯＦＦのときに連結を解除する、少なくとも１つの非円形歯車対用クラッチと、
を備え、
前記非円形歯車対は、
前記入力部材と前記出力部材との間に前記非円形歯車対が連結され、前記非円形歯車対の一方が１回転し、前記非円形歯車対の他方が１回転以上回転して前記非円形歯車対の噛み合いが一巡するときに、
前記非円形歯車対の噛み合いにより前記入力部材と前記出力部材との間の減速比が、前記入力部材と前記出力部材との間に少なくとも２つの前記歯車対がそれぞれ連結されたときの前記入力部材と前記出力部材との間の減速比と同じになる、少なくとも２つの定速噛み合い区間と、
隣り合う前記定速噛み合い区間の間において、前記非円形歯車対の噛み合いにより前記入力部材と前記出力部材との間の減速比が、隣り合う前記定速噛み合い区間の一方の減速比から隣り合う前記定速噛み合い区間の他方の減速比まで変化する、少なくとも２つの変速噛み合い区間と、
を含む、変速機を用いて、
前記入力部材と前記出力部材との間に１つの前記歯車対のみが連結された第１の状態から、前記入力部材と前記出力部材との間に前記非円形歯車対のみが連結され前記変速噛み合い区間で噛み合う中間状態を経て、前記入力部材と前記出力部材との間に他の一つの前記歯車対のみが連結された第２の状態に切り替えることにより、回転する前記入力部材と前記出力部材との間の減速比を切り替える際に、
前記非円形歯車対が前記定速噛み合い区間で噛み合い、前記入力部材と前記出力部材の間に前記歯車対を連結する場合の前記入力部材と前記出力部材との間の減速比と前記入力部材と前記出力部材の間に前記非円形歯車対を連結する場合の前記入力部材と前記出力部材との間の減速比とが同一であり、当該歯車対用の前記クラッチと当該非円形歯車対用の前記非円形歯車対用クラッチのいずれか一方がＯＮであり、かつ、他方がＯＦＦである状態から、前記一方をＯＦＦにした後に前記他方をＯＮにする工程を含み、
前記他方は、位相が合う方向に駆動側と被動側が相対移動可能であれば駆動側と被動側の位相がずれていてもＯＮにすることができる噛み合いクラッチであることを特徴とする、非円形歯車対を用いた変速機の変速方法。 An input member rotatably supported;
An output member rotatably supported;
At least two gear pairs, each disposed between the input member and the output member, and having a constant reduction ratio when coupled between the input member and the output member;
Between the input member and the output member, at least two of the gear pairs, each connected when ON, and at least two clutches released when OFF;
At least one non-circular gear pair that is disposed between the input member and the output member and has a variable reduction ratio when coupled between the input member and the output member;
At least one non-circular gear pair clutch that connects the non-circular gear pair between the input member and the output member when ON and releases the connection when OFF;
With
The non-circular gear pair is
The non-circular gear pair is connected between the input member and the output member, and one of the non-circular gear pair rotates once and the other of the non-circular gear pair rotates one or more times, thereby the non-circular gear pair. When the mating of the pair is complete,
The input member has a reduction ratio between the input member and the output member due to the engagement of the non-circular gear pair, and at least two of the gear pairs are connected between the input member and the output member. And at least two constant speed meshing sections that have the same reduction ratio between the output member and the output member;
Between the adjacent constant speed meshing sections, the reduction ratio between the input member and the output member due to the meshing of the non-circular gear pair is adjacent to the reduction ratio of one of the adjacent constant speed meshing sections. At least two shifting mesh sections that change to the other reduction ratio of the constant speed mesh section;
Including transmission, including
From the first state in which only one gear pair is connected between the input member and the output member, only the non-circular gear pair is connected between the input member and the output member, and the speed change meshing is performed. By switching to a second state in which only one other pair of gears is connected between the input member and the output member through an intermediate state that meshes in a section, the input member and the output member that rotate When switching the reduction ratio between
The reduction ratio between the input member and the output member when the non-circular gear pair meshes in the constant speed meshing section, and the gear pair is connected between the input member and the output member, and the input member. When the non-circular gear pair is connected between the output members, the reduction ratio between the input member and the output member is the same, the clutch for the gear pair and the non-circular gear pair From the state where either one of the non-circular gear pair clutch is ON and the other is OFF, the method includes the step of turning the other ON after turning the one OFF.
The other is a non-circular clutch, which can be turned on even if the driving side and the driven side are out of phase if the driving side and the driven side can move relative to each other in the phase matching direction. A speed change method for a transmission using a gear pair. 前記クラッチがＯＮであるときに、前記入力部材と前記出力部材との間に連結された前記歯車対と減速比が一致する前記定速噛み合い区間で前記非円形歯車対が噛み合っている間に前記クラッチをＯＦＦにした後、前記非円形歯車対用クラッチをＯＮにすることにより、前記第１の状態から前記中間状態に切り替えることを特徴とする、請求項１に記載の非円形歯車対を用いた変速機の変速方法。   When the clutch is ON, the non-circular gear pair is engaged with the non-circular gear pair in the constant-speed meshing section in which the reduction ratio matches the gear pair connected between the input member and the output member. The non-circular gear pair according to claim 1, wherein the non-circular gear pair is switched from the first state to the intermediate state by turning on the non-circular gear pair clutch after the clutch is turned off. The shifting method of the existing transmission. 前記クラッチがＯＮであるならば前記入力部材と前記出力部材との間に連結される前記歯車対の減速比と一致する前記定速噛み合い区間で前記非円形歯車対が噛み合っている間に前記非円形歯車対用クラッチをＯＦＦにした後に、前記クラッチをＯＮにすることにより、前記中間状態から前記第２の状態に切り替えることを特徴とする、請求項１又は２に記載の非円形歯車対を用いた変速機の変速方法。   If the clutch is ON, the non-circular gear pair is engaged while the non-circular gear pair is engaged in the constant-speed engagement section that matches the reduction ratio of the gear pair connected between the input member and the output member. The non-circular gear pair according to claim 1 or 2, wherein the non-circular gear pair is switched from the intermediate state to the second state by turning on the clutch after turning off the clutch for the circular gear pair. The transmission method used for the transmission. 前記入力部材と前記出力部材とは、それぞれ、第１部分と第２部分とを含み、
前記歯車対は、前記入力部材の前記第１部分と前記出力部材の前記第１部分との間に配置され、
前記非円形歯車対は、前記入力部材の前記第２部分と前記出力部材の前記第２部分との間に配置され、
前記変速機は、
前記入力部材の前記第１部分と前記入力部材の前記第２部分とを回転伝達可能に結合する第１の増減速装置と、
前記出力部材の前記第１部分と前記出力部材の前記第２部分とを回転伝達可能に結合する第２の増減速装置と、
をさらに備え、
前記非円形歯車対用クラッチは、前記第１の増減速装置と前記入力部材の前記第２部分と前記非円形歯車対と前記出力部材の前記第２部分と前記第２の増減速装置とを介して前記入力部材の前記第１部分と前記出力部材の前記第１部分との間を解除可能に連結し、
前記非円形歯車対は、前記入力部材の前記第１部分と前記出力部材の前記第１部分との間に前記非円形歯車対が連結され、
前記非円形歯車対の一方が１回転し、前記非円形歯車対の他方が１回転以上回転して前記非円形歯車対の噛み合いが一巡するときに、
前記定速噛み合い区間において、前記非円形歯車対の噛み合いにより前記入力部材の前記第１部分と前記出力部材の前記第１部分との間の減速比が、前記入力部材の前記第１部分と前記出力部材の前記第１部分との間に前記歯車対が連結されたときの前記入力部材の前記第１部分と前記出力部材の前記第１部分との間の減速比と同じになり、
前記変速噛み合い区間において、前記非円形歯車対の噛み合いにより前記入力部材の前記第１部分と前記出力部材の前記第１部分との間の減速比が、隣り合う前記定速噛み合い区間の一方の減速比から隣り合う前記定速噛み合い区間の他方の減速比まで変化することを特徴とする、請求項１乃至３のいずれか一つに記載の非円形歯車対を用いた変速機の変速方法。 The input member and the output member each include a first portion and a second portion,
The gear pair is disposed between the first portion of the input member and the first portion of the output member;
The non-circular gear pair is disposed between the second portion of the input member and the second portion of the output member;
The transmission is
A first acceleration / deceleration device that couples the first part of the input member and the second part of the input member so as to be able to transmit rotation;
A second speed increasing / decreasing device that couples the first part of the output member and the second part of the output member so as to be able to transmit rotation;
Further comprising
The non-circular gear pair clutch includes the first speed increasing / decreasing device, the second portion of the input member, the non-circular gear pair, the second portion of the output member, and the second speed increasing / decreasing device. The first part of the input member and the first part of the output member are releasably connected via,
The non-circular gear pair is connected between the first portion of the input member and the first portion of the output member,
When one of the non-circular gear pairs rotates once, the other of the non-circular gear pairs rotates one or more times, and the meshing of the non-circular gear pairs makes a round,
In the constant speed meshing section, the reduction ratio between the first portion of the input member and the first portion of the output member due to meshing of the non-circular gear pair is such that the first portion of the input member and the first portion of the input member are A reduction ratio between the first portion of the input member and the first portion of the output member when the gear pair is coupled to the first portion of the output member;
In the shift meshing section, the reduction ratio between the first part of the input member and the first part of the output member is reduced by one of the adjacent constant speed meshing sections due to the meshing of the non-circular gear pair. 4. The speed change method for a transmission using a non-circular gear pair according to claim 1, wherein the ratio changes from the ratio to the other reduction ratio of the adjacent constant speed meshing sections. 5.
JP2010282040A 2010-12-17 2010-12-17 Transmission method of transmission using non-circular gear pair Expired - Fee Related JP5621575B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2010282040A JP5621575B2 (en) 2010-12-17 2010-12-17 Transmission method of transmission using non-circular gear pair

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2010282040A JP5621575B2 (en) 2010-12-17 2010-12-17 Transmission method of transmission using non-circular gear pair

Publications (2)

Publication Number Publication Date
JP2012127483A JP2012127483A (en) 2012-07-05
JP5621575B2 true JP5621575B2 (en) 2014-11-12

Family

ID=46644743

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2010282040A Expired - Fee Related JP5621575B2 (en) 2010-12-17 2010-12-17 Transmission method of transmission using non-circular gear pair

Country Status (1)

Country Link
JP (1) JP5621575B2 (en)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3707374B2 (en) * 2000-03-30 2005-10-19 トヨタ自動車株式会社 Always-mesh transmission for vehicles
JP3752435B2 (en) * 2001-07-12 2006-03-08 株式会社日立製作所 Control device for automatic transmission
JP4014041B2 (en) * 2001-11-08 2007-11-28 株式会社日立製作所 Gear-type transmission control device and gear-type transmission control method
JP2003156137A (en) * 2001-11-26 2003-05-30 Hitachi Ltd Gear change control method for vehicle and gear change controller for vehicle
JP4015408B2 (en) * 2001-11-26 2007-11-28 株式会社日立製作所 Control method and control apparatus for automobile
JP2004069030A (en) * 2002-08-09 2004-03-04 Fuji Heavy Ind Ltd Automatic transmission
WO2008062718A1 (en) * 2006-11-22 2008-05-29 Kyoto University Transmission and gear changing method
JP2007085557A (en) * 2006-12-27 2007-04-05 Hitachi Ltd Controller for automobile
JP2009275796A (en) * 2008-05-14 2009-11-26 Aisin Ai Co Ltd Transmission
JP5321961B2 (en) * 2009-02-09 2013-10-23 いすゞ自動車株式会社 transmission
JP5548899B2 (en) * 2009-02-09 2014-07-16 いすゞ自動車株式会社 transmission
JP5165035B2 (en) * 2010-08-20 2013-03-21 日立オートモティブシステムズ株式会社 Vehicle control apparatus and control method

Also Published As

Publication number Publication date
JP2012127483A (en) 2012-07-05

Similar Documents

Publication Publication Date Title
JP4918705B2 (en) Transmission and transmission method
US7661331B2 (en) Shifting device for dual clutch transmission
JP5287576B2 (en) Vehicle drive device
JP5357840B2 (en) Electric tool
CN102966727B (en) Control system of transmission
JP2005155902A (en) Double clutch transmission
JP6023487B2 (en) Vehicle automated manual transmission
JPWO2010100987A1 (en) Parking lock device for transmission
JPWO2016199521A1 (en) Speed change mechanism
JP6517502B2 (en) Two-speed transmission
JP5621575B2 (en) Transmission method of transmission using non-circular gear pair
EP2088343A2 (en) Synchromesh mechanism and synchromesh transmission
JP5548899B2 (en) transmission
JP5321961B2 (en) transmission
JP5403276B2 (en) Transmission using non-circular gear element pairs
JP6607075B2 (en) Always meshing transmission
JP5791024B2 (en) Transmission with non-circular gear pair
JP5379497B2 (en) Rotation transmission equipment
JP6414476B2 (en) Shift device for automatic transmission
JP2015172431A (en) transmission
JP5733714B2 (en) Transmission with non-circular gear pair
JP5853007B2 (en) Transmission control device
WO2014208214A1 (en) Shifting mechanism for multidisc transmission
JP6379218B2 (en) Continuously variable transmission
JP2021196042A (en) Dog clutch

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20131211

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A821

Effective date: 20131211

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20140820

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20140904

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20140908

R150 Certificate of patent or registration of utility model

Ref document number: 5621575

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees