JPH0592565U - Planetary continuously variable transmission - Google Patents
Planetary continuously variable transmissionInfo
- Publication number
- JPH0592565U JPH0592565U JP3846892U JP3846892U JPH0592565U JP H0592565 U JPH0592565 U JP H0592565U JP 3846892 U JP3846892 U JP 3846892U JP 3846892 U JP3846892 U JP 3846892U JP H0592565 U JPH0592565 U JP H0592565U
- Authority
- JP
- Japan
- Prior art keywords
- planetary
- planetary gear
- gear
- continuously variable
- variable transmission
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Retarders (AREA)
- Transmission Devices (AREA)
Abstract
(57)【要約】
〔目的〕 変速比の選択範囲の広い遊星無段変速機を提
供する。
〔構成〕 入力軸２６を連結する遊星差動機構１４と出
力軸３２を連結する遊星歯車機構２０を同軸上に配置し
て入出力軸２６、３２が同一方向に回転するよう設定し
た遊星無段変速装置において、遊星歯車機構２０を構成
する遊星ギアを二段遊星ギア３４にするとともに、各々
の遊星ギア３４ａ、３４ｂをワンウェイクラッチ３６で
結合したことを特徴とする遊星無段変速装置。
(57) [Summary] [Purpose] To provide a planetary continuously variable transmission with a wide selection range of gear ratios. [Structure] A planetary stepless mechanism in which the planetary differential mechanism 14 connecting the input shaft 26 and the planetary gear mechanism 20 connecting the output shaft 32 are coaxially arranged so that the input / output shafts 26, 32 rotate in the same direction. A planetary continuously variable transmission characterized in that, in the transmission, a planetary gear that constitutes the planetary gear mechanism 20 is a two-stage planetary gear 34, and the planetary gears 34a and 34b are connected by a one-way clutch 36.
Description
【０００１】[0001]
本考案は、遊星無段変速装置に関するものである。 The present invention relates to a planetary continuously variable transmission.
【０００２】[0002]
遊星差動機構と遊星歯車機構とを組み合わせた遊星無段変速装置は大きな変速 比を無段で取れることから、走行車輛の変速装置等によく使用されている。図５ はその一例を示す説明図であるが、遊星配置した傘形コーン１０の外周面に変速 リング１２を摺接した遊星差動機構１４と太陽ギア１６に遊星ギア１８を噛み合 わせた遊星歯車機構２０とを組み合わせたものである。即ち、傘形コーン１０に は入力円板２２と出力円板２４とが圧接されており、変速リング１２の位置を変 えることで入力円板２２に対する出力円板２４の回転比が変わるようになってい る。 A planetary continuously variable transmission, which is a combination of a planetary differential mechanism and a planetary gear mechanism, is widely used as a transmission for traveling vehicles, etc., because it can continuously achieve a large gear ratio. FIG. 5 is an explanatory view showing an example thereof. A planetary differential mechanism 14 in which a transmission ring 12 is slidably contacted with an outer peripheral surface of an umbrella-shaped cone 10 arranged in a planet, and a planetary gear 18 and a planetary gear 18 are meshed with a planetary gear 18. This is a combination with the gear mechanism 20. That is, the input disc 22 and the output disc 24 are pressed against the umbrella-shaped cone 10, and the rotation ratio of the output disc 24 to the input disc 22 is changed by changing the position of the transmission ring 12. Is becoming.
【０００３】 この場合、入力円板２２には入力軸２６が連結されているとともに、入力軸２ ６には前記した太陽ギア１６が形成されている。一方、出力円板２４は内歯歯車 ２８に連結されており、この内歯歯車２８と太陽ギア１６との間に前記した遊星 ギア１８が噛み合っている。又、遊星ギア１８は腕３０に遊嵌しており、この腕 ３０が出力軸３２を形成しているものである。In this case, an input shaft 26 is connected to the input disc 22 and the sun gear 16 is formed on the input shaft 26. On the other hand, the output disc 24 is connected to an internal gear 28, and the planet gear 18 is meshed between the internal gear 28 and the sun gear 16. The planet gear 18 is loosely fitted on the arm 30, and the arm 30 forms an output shaft 32.
【０００４】[0004]
このような遊星無段変速装置は大きな変速比が無段で取れ、しかもコンパクト な設計になるから、走行車輛等の変速装置によく使用されるのは前記したとおり であるが、一方で遊星歯車機構２０は一組であるから、これらの歯数のみが変速 比に関与し、変速比の選択範囲が狭められるのは否めない。 本考案は、このような課題を解決するものであって、要するに、変速比の選択 や構造設計の自由度を増す遊星無段変速装置を企図したものである。 Since such a planetary continuously variable transmission can achieve a large gear ratio continuously and has a compact design, it is often used in a transmission such as a traveling vehicle as described above. Since the mechanism 20 is a set, it is undeniable that only these numbers of teeth are involved in the gear ratio and the selection range of the gear ratio is narrowed. The present invention solves such a problem and, in short, is intended to provide a planetary continuously variable transmission that increases the degree of freedom in selection of gear ratio and structural design.
【０００５】[0005]
以上の課題を解決するため、本考案は、入力軸を連結する遊星差動機構と出力 軸を連結する遊星歯車機構を同軸上に配置して入出力軸が同一方向に回転するよ う設定した遊星無段変速装置において、遊星歯車機構を構成する遊星ギアを二段 遊星ギアにするとともに、各々の遊星ギアをワンウェイクラッチで結合したこと を特徴とする遊星無段変速装置を提供するものである。 In order to solve the above problems, the present invention sets the planetary differential mechanism that connects the input shaft and the planetary gear mechanism that connects the output shaft on the same axis so that the input and output shafts rotate in the same direction. In a planetary continuously variable transmission, there is provided a planetary continuously variable transmission characterized in that a planetary gear that constitutes a planetary gear mechanism is a two-stage planetary gear and that each planetary gear is connected by a one-way clutch. .
【０００６】[0006]
以上の手段をとることにより、即ち、遊星歯車機構を構成する遊星ギアを二段 遊星ギアにしたものであるから、その変速比の選択の幅が広い。そして、両遊星 ギアはワンウェイクラッチで結合したものであるから、組立の際の位相合わせが 容易である。 By adopting the above means, that is, because the planetary gears constituting the planetary gear mechanism are two-stage planetary gears, the range of selection of the gear ratio is wide. Since both planetary gears are connected by a one-way clutch, phase alignment during assembly is easy.
【０００７】[0007]
図１は本考案に係る遊星無段変速装置の説明図であるが、遊星差動機構機１４ 及び遊星歯車機構２０の概略の構成は前記と同じであるが、違うのは、遊星歯車 機構２０を構成する遊星ギア１８の代わりに第一遊星ギア３４ａと第二遊星ギア ３４ｂとからなる二段遊星ギア３４で構成した点である。このようにすると、第 一遊星ギア３４ａと第二遊星ギア３４ｂとの位相合わせが問題になるが、これが 容易なように、第二遊星ギア３４ｂをワンウェイクラッチ３６を介して第一遊星 ギア３４ａに結合するのである。 FIG. 1 is an explanatory view of a planetary continuously variable transmission according to the present invention. The schematic configurations of the planetary differential mechanism 14 and the planetary gear mechanism 20 are the same as those described above, except that the planetary gear mechanism 20 is different. Instead of the planetary gear 18 constituting the above, a two-stage planetary gear 34 including a first planetary gear 34a and a second planetary gear 34b is used. In this case, the phase alignment between the first planetary gear 34a and the second planetary gear 34b becomes a problem, but to facilitate this, the second planetary gear 34b is connected to the first planetary gear 34a via the one-way clutch 36. Unite.
【０００８】 図２は他の実施例を示す説明図であるが、この実施例のものは遊星差動機構１ ４と切換歯車機構３８とからなる変速装置にブレーキ機構４０を組み合わせたデ ッドマンシステムであるが、切換歯車機構３８は切換ギア４２を二つの従動ギア ４４、４６にスライドして噛み合わせるように構成してある。この場合、各従動 ギア４４、４６をその軸４８、５０に結合する場合にバックラッシュ機構を持た せるようにしたものである。FIG. 2 is an explanatory view showing another embodiment. In this embodiment, a deadman in which a brake mechanism 40 is combined with a transmission composed of a planetary differential mechanism 14 and a switching gear mechanism 38. In the system, the switching gear mechanism 38 is configured so that the switching gear 42 is slidably engaged with the two driven gears 44 and 46. In this case, a backlash mechanism is provided when each driven gear 44, 46 is connected to its shaft 48, 50.
【０００９】 図３及び図４はその具体例を示す断面図であるが、例えば、軸４８、５０に設 けられるキーやドグ等の駆動手段５２が入る相手方の孔５４を回転方向前後に隙 間を設け、この隙間の中に駆動手段５２の両側に弾性体５６等を挿入したものが 考えられる。このようにすることで、切換ギア４２の切換えがスムーズに行われ る利点がある。FIG. 3 and FIG. 4 are cross-sectional views showing a specific example thereof. For example, a hole 54 of the other side into which a driving means 52 such as a key or a dog provided on the shafts 48 and 50 is inserted is formed in the front and rear in the rotation direction. It is conceivable that a space is provided and the elastic bodies 56 and the like are inserted into both sides of the drive means 52 in this gap. By doing so, there is an advantage that the switching gear 42 can be smoothly switched.
【００１０】[0010]
以上、本考案は、前記したものであるから、即ち、遊星無段変速装置の遊星歯 車機構を構成する遊星ギアを二段遊星ギアにしたものであるから、設計の自由度 が増し、それだけ変速比の選択範囲が広まる。特に、出力軸の回転数を従来のも のよりも高くすることが可能である。又、二段遊星ギア同士の結合はワンウェイ クラッチを用いて行うものであるから、位相合わせが容易にでき、その分、各ギ アの加工に精度を要しない。このことは位相誤差による振動、騒音の低減にも役 立つ。 As described above, since the present invention is the one described above, that is, the planetary gear that constitutes the planetary gear mechanism of the planetary continuously variable transmission is a two-stage planetary gear, the degree of freedom in design is increased, and only that. Wide selection range of gear ratio. In particular, it is possible to increase the rotation speed of the output shaft higher than the conventional one. In addition, since the two-stage planetary gears are connected to each other by using a one-way clutch, the phase can be easily adjusted, and the precision of machining each gear is not required. This also helps reduce vibration and noise due to phase error.
【図１】本考案に係る遊星無段変速装置の説明図であ
る。FIG. 1 is an explanatory view of a planetary continuously variable transmission according to the present invention.
【図２】本考案の他の実施例を示す説明図である。FIG. 2 is an explanatory view showing another embodiment of the present invention.
【図３】本考案の他の実施例を示す断面図である。FIG. 3 is a cross-sectional view showing another embodiment of the present invention.
【図４】本考案の他の実施例を示す断面図である。FIG. 4 is a cross-sectional view showing another embodiment of the present invention.
【図５】従来の遊星無段変速装置の説明図である。FIG. 5 is an explanatory diagram of a conventional planetary continuously variable transmission.
１４ 遊星差動機構 １８ 遊星ギア ２０ 遊星歯車機構 ２６ 入力軸 ３２ 出力軸 ３４ 二段遊星ギア ３６ ワンウェイクラッチ 14 planetary differential mechanism 18 planetary gear 20 planetary gear mechanism 26 input shaft 32 output shaft 34 two-stage planetary gear 36 one-way clutch
Claims (1)
を連結する遊星歯車機構を同軸上に配置して入出力軸が
同一方向に回転するよう設定した遊星無段変速装置にお
いて、遊星歯車機構を構成する遊星ギアを二段遊星ギア
にするとともに、各々の遊星ギアをワンウェイクラッチ
で結合したことを特徴とする遊星無段変速装置。1. A planetary continuously variable transmission in which a planetary differential mechanism for connecting an input shaft and a planetary gear mechanism for connecting an output shaft are coaxially arranged so that the input and output shafts rotate in the same direction. A planetary continuously variable transmission characterized in that a planetary gear that constitutes a gear mechanism is a two-stage planetary gear, and each planetary gear is connected by a one-way clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3846892U JPH0592565U (en) | 1992-05-11 | 1992-05-11 | Planetary continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3846892U JPH0592565U (en) | 1992-05-11 | 1992-05-11 | Planetary continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0592565U true JPH0592565U (en) | 1993-12-17 |
Family
ID=12526080
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3846892U Pending JPH0592565U (en) | 1992-05-11 | 1992-05-11 | Planetary continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0592565U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007024297A (en) * | 2005-07-21 | 2007-02-01 | Mikuni Corp | Power output device in two-wheeler |
| JP2012096775A (en) * | 2010-10-07 | 2012-05-24 | Ntn Corp | Hub motor device for power-assisted bicycle |
| KR20190037002A (en) * | 2017-09-28 | 2019-04-05 | 최형진 | Power tansmission device |
-
1992
- 1992-05-11 JP JP3846892U patent/JPH0592565U/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007024297A (en) * | 2005-07-21 | 2007-02-01 | Mikuni Corp | Power output device in two-wheeler |
| JP2012096775A (en) * | 2010-10-07 | 2012-05-24 | Ntn Corp | Hub motor device for power-assisted bicycle |
| KR20190037002A (en) * | 2017-09-28 | 2019-04-05 | 최형진 | Power tansmission device |
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