JPH0150783B2 - - Google Patents
Info
- Publication number
- JPH0150783B2 JPH0150783B2 JP61164703A JP16470386A JPH0150783B2 JP H0150783 B2 JPH0150783 B2 JP H0150783B2 JP 61164703 A JP61164703 A JP 61164703A JP 16470386 A JP16470386 A JP 16470386A JP H0150783 B2 JPH0150783 B2 JP H0150783B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- eccentric cam
- pawl
- ratchet
- carrier
- 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
Links
- 230000005540 biological transmission Effects 0.000 claims description 34
- 210000000078 claw Anatomy 0.000 description 14
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Landscapes
- Arrangement Or Mounting Of Control Devices For Change-Speed Gearing (AREA)
- Structure Of Transmissions (AREA)
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、自動二輪車等の原動機に接続する無
段変速装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a continuously variable transmission device connected to a prime mover of a motorcycle or the like.
（従来の技術）
従来の自動二輪車の変速装置としては、主に歯
車式変速機が多用されており、そしてこの種の歯
車式変速機はかなり大型であるため、エンジンと
隣接して設けられているものが多い。(Prior Art) As a conventional transmission for a motorcycle, a gear type transmission is mainly used, and since this type of gear type transmission is quite large, it is necessary to install it adjacent to the engine. There are many.
（発明が解決しようとする問題点）
しかしながら従来の歯車式変速機は有段変速で
あり、変速範囲を大きくするには、変速段数を多
くしなければならないから、変速操作が繁雑にな
る上に、装置全体が大きくなるという問題点があ
つた。(Problems to be Solved by the Invention) However, conventional gear type transmissions have stepped transmissions, and in order to widen the shifting range, the number of gears must be increased, which makes the shifting operation complicated and However, there was a problem that the entire device became large.
上述の問題点を解決するため本出願人は先に、
爪式無段変速機構と、減速型芯戻し歯車機構と、
遊星歯車式増速機構とを中心軸回りに一体的に結
合して、二輪車の駆動輪のハブ内に納まるよにし
た自動二輪車用無段変速装置を出願したが、この
装置は爪式無段変速機構を使用するものであるか
ら、そのままではエンジンブレーキが使用できな
いという問題点があつた。 In order to solve the above problems, the applicant first
A claw-type continuously variable transmission mechanism, a reduction type centering gear mechanism,
The patent application was filed for a continuously variable transmission device for motorcycles in which a planetary gear type speed increasing mechanism is integrally connected around the central axis and is housed in the hub of the drive wheel of the motorcycle, but this device is a claw type continuously variable transmission device. Since it uses a transmission mechanism, there was a problem in that engine braking could not be used as it was.
（問題点を解決するための手段）
上述の問題点を解決するため本発明において
は、内側偏心カムと外側偏心カムとの組み合せに
より偏心量を調整自在にした偏心カムを中心軸に
設け、この偏心カムを外包するように中空円筒状
に形成した入力側の駆動回転部材の内周に内歯ラ
チエツトを設け、この内歯ラチエツトに噛合する
爪の基部を前記偏心カムに回転自在に設けた爪キ
ヤリヤに析支し、この爪キヤリヤの外周に設けた
歯車を前記内側偏心カムに設けた伝動歯車を介し
て前記中心軸に設けた遊星キヤリヤの内歯歯車と
噛合し、この遊星キヤリヤに設けた遊星歯車を前
記駆動回転部材に設けた内歯々車に噛合すると共
に出力側の太陽歯車に噛合し、前記駆動回転部材
を外包するハブを前記太陽歯車と一体的に結合
し、このハブと駆動回転部材との間に一方向クラ
ツチを設けて二輪車用無段変速装置を構成する。(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, an eccentric cam whose eccentricity can be freely adjusted by a combination of an inner eccentric cam and an outer eccentric cam is provided on the central shaft. An internal toothed ratchet is provided on the inner periphery of an input-side driving rotation member formed in a hollow cylindrical shape so as to enclose an eccentric cam, and a claw that engages with this internal toothed ratchet is rotatably provided on the eccentric cam. A gear provided on the outer periphery of the pawl carrier meshes with an internal gear of the planetary carrier provided on the central shaft via a transmission gear provided on the inner eccentric cam. A planetary gear meshes with an internal gear provided on the drive rotation member and also meshes with a sun gear on the output side, and a hub enclosing the drive rotation member is integrally coupled with the sun gear, and the hub and the drive A one-way clutch is provided between the rotating member and a continuously variable transmission for a two-wheeled vehicle.
（作 用）
上述のように本発明においては、爪式無段変速
機構と、減速型芯戻し歯車機構と、遊星歯車式増
速機構とを中心軸回りに一体的に結合して、例え
ば二輪車の後輪のハブ内に納まるようにしたか
ら、非常に小型で、しかも入力回転数に対する出
力回転数を、例えば１：１から１：０までの広範
囲で無段変速ができるから、変速シヨツクのない
広い範囲の変速を容易に行うことができる。そし
て装置全体がハブ内に納まるため、小型軽量であ
る上に、レイアウトも非常に容易になる。(Function) As described above, in the present invention, the pawl type continuously variable transmission mechanism, the reduction type centering gear mechanism, and the planetary gear type speed increase mechanism are integrally connected around the central axis, so that, for example, a two-wheeled vehicle Because it fits inside the hub of the rear wheel, it is very compact, and the output speed relative to the input speed can be continuously variable over a wide range, for example from 1:1 to 1:0, making it possible to use a variable speed shock. You can easily change gears over a wide range. Since the entire device is housed within the hub, it is not only small and lightweight, but also extremely easy to layout.
また本発明においては、前記爪式無段変速機構
の入力部材である駆動回転部材を外包するハブを
前記遊星歯車式増速機構の出力部材である太陽歯
車と一体的に結合し、このハブと駆動回転部材と
の間に一方向クラツチを設けたから、これによつ
てエンジンブレーキも有効に作用させることがで
きる。 Further, in the present invention, a hub enclosing a drive rotating member which is an input member of the claw type continuously variable transmission mechanism is integrally coupled with a sun gear which is an output member of the planetary gear type speed increasing mechanism. Since a one-way clutch is provided between the drive rotating member and the rotating member, engine braking can also be effectively applied.
（実施例）
以下、図面について本発明の二輪車用無段変速
装置の実施例を説明する。(Example) Hereinafter, an example of the continuously variable transmission device for a two-wheeled vehicle of the present invention will be described with reference to the drawings.
図中１は二輪車の車体フレームのチエンステ
ー、１ａは後爪、２はバツクホーク、３は後爪１
ａにロツクナツト４，５により固定した後輪ハブ
軸（中心軸）、６はベアリング７を介して回転自
在に嵌装した後輪ハブ、８はスポークである。 In the figure, 1 is the chain stay of the motorcycle body frame, 1a is the rear claw, 2 is the back hawk, and 3 is the rear claw 1.
A is a rear wheel hub shaft (center shaft) fixed by lock nuts 4 and 5, 6 is a rear wheel hub rotatably fitted via a bearing 7, and 8 is a spoke.
本実施例においては、後輪ハブ６の第１図にお
ける左側の軸受部に中空円筒状のボス部６ａを突
設し、このボス部６ａの先端部の外周に太陽歯車
９を形成する。 In this embodiment, a hollow cylindrical boss portion 6a is provided protruding from the left bearing portion of the rear wheel hub 6 in FIG. 1, and a sun gear 9 is formed on the outer periphery of the tip of the boss portion 6a.
またスプロケツト１０とボルト１１により一体
的に結合したほぼ中空円筒状の駆動回転部材１２
を軸受１３，１４を介して後輪ハブ６に対して回
転自在に設け、この駆動回転部材１２の第１図に
おける左側の内周部に内歯々車１５をボルト１６
により固定して設ける。 Further, a substantially hollow cylindrical drive rotating member 12 is integrally connected to the sprocket 10 by a bolt 11.
is provided rotatably with respect to the rear wheel hub 6 via bearings 13 and 14, and an internal toothed wheel 15 is attached to a bolt 16 on the inner circumferential portion of the left side of the drive rotating member 12 in FIG.
It is fixedly provided.
また前記ボス部６ａ内の後輪ハブ軸３にほぼ円
板状の遊星キヤリヤ１７をラジアル軸受１８およ
びスラスト軸受１９を介して回転自在に設ける。
２０はロツクナツトである。遊星キヤリヤ１７に
は第９図に示すように４個の遊星歯車２１を軸２
２によりそれぞれ回転自在に設け、これらの遊星
歯車２１をそれぞれ前記太陽歯車９と噛合させる
と共に、内歯々車１５と噛合させ、遊星キヤリヤ
１７の外周縁部に内歯々車１７ａを形成する。 Further, a substantially disk-shaped planetary carrier 17 is rotatably provided on the rear wheel hub shaft 3 within the boss portion 6a via a radial bearing 18 and a thrust bearing 19.
20 is a rock nut. The planetary carrier 17 has four planetary gears 21 attached to the shaft 2, as shown in FIG.
The planetary gears 21 are each meshed with the sun gear 9 and the internal gear 15, thereby forming an internal gear 17a on the outer peripheral edge of the planetary carrier 17.
また第４図に示すように中心軸（後輪ハブ軸）
３に対してl1だけ偏心させた円筒状の内側偏心カ
ム２３と、内側偏心カム２３に対してl2だけ偏心
させた円筒状の外側偏心カム２４とを回転自在に
嵌合したものを、第１図における遊星キヤリヤ１
７の右側の後輪ハブ軸３に嵌装し、遊星キヤリヤ
１７と外側偏心カム２４との間の内側偏心カム２
３にラジアル軸受２５およびスラスト軸受２６を
介して伝動歯車２７を設け、この伝動歯車２７の
外歯々車２７ａを前記内歯々車１７ａと噛合さ
せ、この外歯々車２７ａの内周部に内歯々車２７
ｂを形成する。なお２８は伝動歯車２７と外側偏
心カム２４との間に設けた仕切板で、外側偏心カ
ム２４と一体的に回転するようになつている。 Also, as shown in Figure 4, the center axis (rear wheel hub axis)
A cylindrical inner eccentric cam 23 that is eccentric by l 1 with respect to the inner eccentric cam 23 and a cylindrical outer eccentric cam 24 that is eccentric by l 2 with respect to the inner eccentric cam 23 are rotatably fitted, Planetary carrier 1 in Figure 1
The inner eccentric cam 2 is fitted onto the rear wheel hub axle 3 on the right side of 7 and is located between the planet carrier 17 and the outer eccentric cam 24
3 is provided with a transmission gear 27 via a radial bearing 25 and a thrust bearing 26, and an external gear 27a of this transmission gear 27 is meshed with the internal gear 17a. Internal gear wheel 27
form b. Note that 28 is a partition plate provided between the transmission gear 27 and the outer eccentric cam 24, and is adapted to rotate integrally with the outer eccentric cam 24.
また外側偏心カム２４の外周部に軸受２９を介
してほぼ中空円筒状の爪キヤリヤ３０を回転自在
に嵌装し、この爪キヤリヤ３０と一体に形成した
歯車３０ａを前記内歯々車２７ｂと噛合するよう
にする。 Further, a substantially hollow cylindrical pawl carrier 30 is rotatably fitted to the outer circumference of the outer eccentric cam 24 via a bearing 29, and a gear 30a formed integrally with the pawl carrier 30 meshes with the internal gear wheel 27b. I'll do what I do.
また爪キヤリヤ３０と対向する駆動回転部材１
２の内周部に一方向クラツチ３１を介して複数列
（本実施例では２列）の内歯ラチエツトリング３
２を並設し、これら各ラチエツトリング３２の内
周面にそれぞれラチエツト３２ａを設けると共
に、ラチエツト３２ａとそれぞれ噛合する複列
で、かつ各列複数個（本実施例では第６図に示す
ように４個）の爪３３の基部を、前記爪キヤリヤ
３０の外周部にピン３４を介して第６図に示すよ
うに左右互い違いに配置して枢支する。また３５
は爪３３の先端を常にラチエツト３２ａに圧接さ
せるためのばねである。 Further, the drive rotating member 1 facing the pawl carrier 30
A plurality of rows (two rows in this embodiment) of internally toothed ratchet rings 3 are connected to the inner circumference of the ratchet ring 2 via a one-way clutch 31.
2 are arranged in parallel, and each ratchet ring 32 is provided with a ratchet 32a on the inner circumferential surface thereof, and each ratchet ring 32 has a double row that meshes with the ratchet ring 32a, and a plurality of ratchets in each row (in this embodiment, as shown in FIG. 6). The bases of the four pawls 33 are pivotally supported on the outer periphery of the pawl carrier 30 via pins 34, arranged alternately on the left and right as shown in FIG. Also 35
is a spring that keeps the tip of the pawl 33 in pressure contact with the ratchet 32a.
なお３６は内歯ラチエツトリング３２の一方の
側面に接して２枚のスナツプリング３７により摺
動自在に挟持された浮動リングで、各爪３３の一
側方に突設した爪先端部３３ａと浮動状態におい
て係合することにより、爪３３とラチエツト３２
ａとの無用の接触を阻止して騒音の発生を防止す
るものである。 Note that 36 is a floating ring that is in contact with one side of the internal toothed ratchet ring 32 and is slidably held between two snap springs 37, and is floating with the claw tip 33a protruding from one side of each claw 33. By engaging in the state, the pawl 33 and the ratchet 32
This prevents noise from being generated by preventing unnecessary contact with a.
また内歯ラチエツトリング３２，３２の間に、
駆動回転部材１２の内周と転接する複数個（本実
施例では第７図に示すように６個）のローラ３８
を介して２個一組の先送りリング３９を回転自在
に設ける。３８ａはローラ３８を先送りリング３
９に枢支する軸である。 Also, between the internal tooth ratchet rings 32, 32,
A plurality of rollers 38 (six in this embodiment as shown in FIG. 7) are in rolling contact with the inner periphery of the drive rotating member 12.
A set of two forwarding rings 39 are rotatably provided via. 38a is the advance ring 3 for the roller 38.
This is the axis that pivots to 9.
そしてこの先送りリング３９をそれぞれ内歯ラ
チエツトリング３２に摩擦接合する。その摩擦接
合手段の一例を説明すると、内歯ラチエツトリン
グ３２，３２の対向側にそれぞれ環状の段部３２
ｂを形成し、これらの段部３２ｂにそれぞれリン
グばね４０を嵌め込むと共に、第７図に示すよう
にリングばね４０の開口端部４０ａをそれぞれ外
方に折り曲げて、これら開口端部４０ａ間に前記
ローラ３８の軸３８ａの一つを挟むようにする。 The advance rings 39 are then frictionally joined to the internally toothed ratchet rings 32, respectively. To explain an example of the friction joining means, an annular step portion 32 is provided on the opposite side of the internally toothed ratchet rings 32, 32, respectively.
b, and fit the ring springs 40 into these stepped portions 32b, respectively, and bend the open ends 40a of the ring springs 40 outward as shown in FIG. One of the shafts 38a of the roller 38 is sandwiched therebetween.
またローラ３８を挟持する左右２個の先送りリ
ング３９間に複数個（本実施例では６個）の爪４
１の基部をそれぞれ円周等分割点に挿入すると共
に、ピン４２によつて先送りリング３９に枢支
し、ばね４３により爪４１の先端が常に内方へ回
動するように付勢する。そしてこれらの爪４１と
噛合するラチエツト４４を前記爪キヤリヤ３０の
中間の外周部にキヤリヤ３０と一体的に設ける。 Furthermore, a plurality of (six in this embodiment) pawls 4 are provided between the two left and right advance rings 39 that sandwich the roller 38.
The bases of the claws 41 are inserted into equally divided points on the circumference, and are pivoted to the advance ring 39 by pins 42, and are urged by springs 43 so that the tips of the claws 41 always rotate inward. A ratchet 44 that engages with these pawls 41 is provided integrally with the pawl carrier 30 at an intermediate outer peripheral portion of the pawl carrier 30.
なおこの連動機構である爪４１とラチエツト４
４は逆に設けてもよい。すなわちキヤリヤ３０側
に爪４１を枢支し、先送りリング３９側にラチエ
ツト４４を形成してもよい。 Note that this interlocking mechanism is the pawl 41 and the ratchet 4.
4 may be provided in reverse. That is, the pawl 41 may be pivotally supported on the carrier 30 side, and the ratchet 44 may be formed on the advance ring 39 side.
また外側偏心カム２４の第１図における右側端
部にフランジ部２４ａを突設すると共に、このフ
ランジ部２４ａに第４図に示すように直径方向に
沿つて長穴４５を設ける。またこのフランジ部２
４ａの外側方に位置する内側偏心カム２３の延長
部に、後輪ハブ軸３を中心とする円形の段部２３
ａを形成すると共に、この段部２３ａの外側に段
部２３ａより大径で段部２３ａと同心の太陽歯車
４６を一体的に形成し、この太陽歯車４６と同一
のリング状の太陽歯車４７を前記段部２３ａに嵌
装すると共に、この太陽歯車４７に突設した突起
４７ａを前記長穴４５に摺動自在に嵌入させる。 Further, a flange portion 24a is provided protruding from the right end portion of the outer eccentric cam 24 in FIG. 1, and an elongated hole 45 is provided in the flange portion 24a along the diameter direction as shown in FIG. Also, this flange part 2
A circular stepped portion 23 centered on the rear wheel hub axle 3 is provided on an extension of the inner eccentric cam 23 located on the outer side of the inner eccentric cam 4a.
a, and a sun gear 46 having a larger diameter than the step 23a and concentric with the step 23a is integrally formed on the outside of the step 23a, and a ring-shaped sun gear 47 identical to this sun gear 46 is formed. The protrusion 47a protruding from the sun gear 47 is fitted into the step portion 23a, and the protrusion 47a is slidably fitted into the elongated hole 45.
またほぼ円板状の固定部材４８のボス部を後輪
ハブ軸３のテーパー部３ａ（第１図参照）に嵌合
すると共にナツト５，４によつて固定するように
し、この固定部材４８の外周部に形成したリング
部の内周に一方向クラツチ４９（第２図参照）を
介してリング状の内歯々車５０を設ける。４９ａ
（第３図参照）は一方向クラツチ４９のラチエツ
ト、４９ｂは爪、４９ｃはばねである。５１はこ
の内歯々車５０のガイドリング、５２はこのガイ
ドリング５１の位置決め用のスナツプリングであ
る。なお５３は固定部材４８と駆動回転部材１２
との間の軸受用ボールである。 Further, the boss portion of the substantially disc-shaped fixing member 48 is fitted into the tapered portion 3a of the rear wheel hub axle 3 (see FIG. 1) and fixed by the nuts 5 and 4. A ring-shaped internal gear 50 is provided on the inner periphery of the ring portion formed on the outer periphery via a one-way clutch 49 (see FIG. 2). 49a
(See FIG. 3) is a ratchet of the one-way clutch 49, 49b is a pawl, and 49c is a spring. Reference numeral 51 represents a guide ring of this internal gear 50, and 52 represents a snap ring for positioning this guide ring 51. Note that 53 indicates the fixed member 48 and the drive rotating member 12.
This is a bearing ball between the
また固定部材４８に第３図に二点鎖線で示すよ
うな円弧状の長孔４８ａを円周三等分位置にそれ
ぞれ設け、これらの長孔４８ａ間の固定部材４８
にそれぞれ軸５４を内側へ向けて突設し、この軸
５４に嵌合した遊星歯車５５をそれぞれ太陽歯車
４６と噛合させると共に、内歯々車５０と噛合さ
せる。 In addition, the fixing member 48 is provided with arc-shaped long holes 48a as shown by two-dot chain lines in FIG.
A shaft 54 is provided to protrude inwardly at each of the shafts 54, and planetary gears 55 fitted on the shafts 54 are meshed with the sun gear 46 and the internal gear 50, respectively.
また固定部材４８の長孔４８ａをカバーするリ
ング状の円板５６ａとレバー５６ｂとをビス５６
ｃにより一体に形成した操作プレート５６を固定
部材４８のボス部に回転自在に嵌合し、この操作
プレート５６に各長孔４８ａを貫通して内側方に
突出する軸５７をそれぞれ設け、これらの軸５７
にそれぞれ遊星歯車５８を嵌装し、各遊星歯車５
８を前記太陽歯車４７と噛合させると共に、内
歯々車５０とも噛合させる。 Further, the ring-shaped disc 56a that covers the elongated hole 48a of the fixing member 48 and the lever 56b are connected with the screw 56.
An operation plate 56 integrally formed with a screw plate 56 is rotatably fitted into the boss portion of the fixing member 48, and a shaft 57 is provided on the operation plate 56 and projects inwardly through each elongated hole 48a. axis 57
A planetary gear 58 is fitted into each planetary gear 5.
8 is meshed with the sun gear 47 and also with the internal gear 50.
なお５９は固定部材４８のボス部に嵌装したカ
ラー、６０はその抜け止め用のスナツプリング、
６１は操作杆、６２は操作杆６１とレバー５６ｂ
との連結軸、６３はスプロケツト１０にかけ渡し
たチエンである。 In addition, 59 is a collar fitted to the boss portion of the fixing member 48, 60 is a snap spring for preventing it from coming off,
61 is the operating rod, 62 is the operating rod 61 and lever 56b
The connecting shaft 63 is a chain that spans the sprocket 10.
また駆動回転部材１２と後輪ハブ６との間に、
第１図および第６図に示すように一方向クラツチ
６４を設ける。６４ａは後輪ハブ６の内周に形成
したラチエツト、６４ｂは基部を駆動回転部材１
２に枢支すると共に、爪先がラチエツト６４ａと
係合すようにした爪、６４ｃはこの爪６４ｂをラ
チエツト６４ａと係合するように付勢するばねで
ある。そしてこの一方向クラツチ６４は後輪ハブ
６が第６図の矢印の方向に回転する場合に、そ
の回転力を駆動回転部材１２に伝えるようにす
る。 Moreover, between the drive rotating member 12 and the rear wheel hub 6,
A one-way clutch 64 is provided as shown in FIGS. 1 and 6. 64a is a ratchet formed on the inner periphery of the rear wheel hub 6, and 64b is a base connected to the drive rotation member 1.
A pawl 64c, which is pivoted to the latch 2 and whose tip engages with the ratchet 64a, is a spring that biases the pawl 64b into engagement with the ratchet 64a. The one-way clutch 64 transmits the rotational force to the drive rotating member 12 when the rear wheel hub 6 rotates in the direction of the arrow in FIG.
つぎに上述のように構成した本発明の実施例の
作用を説明する。まず伝動順序を説明すると、図
示しないエンジンによつて駆動用スプロケツトが
回転し、その回転がチエン６３によりスプロケツ
ト１０およびこれと一体の駆動回転部材１２に伝
えられる。駆動回転部材１２の回転は一方向クラ
ツチ３１を介して内歯ラチエツトリング３２に伝
えられ、さらにラチエツト３２ａより爪３３、ピ
ン３４を介して爪キヤリヤ３０に伝えられる。爪
キヤリヤ３０が回転すると、歯車３０ａが回転
し、第８図に示すようにこれと噛合する内歯々車
２７ｂを介して伝動歯車２７が回転し、さらに外
歯々車２７ａと内歯々車１７ａの噛合によつて遊
星キヤリヤ１７が後輪ハブ軸３を中心にして回転
する。遊星キヤリヤ１７が回転すると、遊星キヤ
リヤ１７、内歯々車１５、遊星歯車２１、および
太陽歯車９からなる遊星歯車式増速装置を介して
太陽歯車９に増速回転が伝えられ、太陽歯車９と
一体の後輪ハブ６が回転することによつて二輪車
の後輪（図示せず）が駆動される。 Next, the operation of the embodiment of the present invention constructed as described above will be explained. First, to explain the transmission sequence, a driving sprocket is rotated by an engine (not shown), and the rotation is transmitted by a chain 63 to the sprocket 10 and the driving rotating member 12 integrated therewith. The rotation of the drive rotating member 12 is transmitted to the internally toothed ratchet ring 32 via the one-way clutch 31, and further transmitted from the ratchet 32a to the pawl carrier 30 via the pawl 33 and pin 34. When the pawl carrier 30 rotates, the gear 30a rotates, and as shown in FIG. 8, the transmission gear 27 rotates via the internal gear 27b that meshes with the gear 30a. 17a rotates the planetary carrier 17 around the rear wheel hub shaft 3. When the planetary carrier 17 rotates, the increased rotation is transmitted to the sun gear 9 via the planetary gear type speed up device consisting of the planetary carrier 17, the internal gear 15, the planetary gear 21, and the sun gear 9. The rear wheels (not shown) of the two-wheeled vehicle are driven by the rotation of the rear wheel hub 6, which is integral with the rear wheel hub 6.
つぎに変速操作について説明すると、二輪車に
取り付けた変速レバー（図示せず）を操作するこ
とにより、第２，３図に示す操作杆６１を矢印Ａ
の方向に移動させると、操作プレート５６が矢印
Ｂの方向に回動するため、軸５７も矢印Ｂの方向
に回動する。この場合二輪車が停止中であれば、
すべての部材が停止している。 Next, explaining the gear shift operation, by operating the gear shift lever (not shown) attached to the motorcycle, the operating rod 61 shown in FIGS. 2 and 3 is moved to the arrow A.
When the operating plate 56 is moved in the direction indicated by arrow B, the shaft 57 is also rotated in the direction indicated by arrow B. In this case, if the motorcycle is stopped,
All parts are stopped.
したがつて軸５７が矢印Ｂの方向に移動する
と、遊星歯車５８が内歯々車５０との噛合によつ
て第３図の矢印Ｃの方向に回転するため、これと
噛合する太陽歯車４７を遊星歯車５８の矢印Ｂ方
向の公転と矢印Ｃの方向の自転によつて第４図の
矢印Ｄの方向に大きく回転させる。 Therefore, when the shaft 57 moves in the direction of arrow B, the planetary gear 58 rotates in the direction of arrow C in FIG. The planetary gear 58 revolves in the direction of arrow B and rotates on its axis in the direction of arrow C, causing a large rotation in the direction of arrow D in FIG. 4.
そして太陽歯車４７は突起４７ａと一体であ
り、この突起４７ａが外側偏心カム２４のフラン
ジ部２４ａに設けた長穴４５と嵌合しているた
め、結局太陽歯車４７が回動すれば内側偏心カム
２３に対して外側偏心カム２４が差動することに
なる。 The sun gear 47 is integrated with a protrusion 47a, and this protrusion 47a fits into an elongated hole 45 provided in the flange portion 24a of the outer eccentric cam 24, so that when the sun gear 47 rotates, the inner eccentric cam The outer eccentric cam 24 moves differentially with respect to the outer eccentric cam 23.
第５図を除く図示の状態は上述の操作の結果、
外側偏心カム２４が最大偏心状態にある場合を示
すものである。 The states shown except in FIG. 5 are the result of the above operations.
This shows the case where the outer eccentric cam 24 is in the maximum eccentric state.
つぎに操作杆６１を前とは逆に矢印Ｅの方向に
操作すると、操作プレート５６および軸５７が矢
印Ｆの方向に回動するから、遊星歯車５８が第３
図の矢印Ｇの方向に回転して太陽歯車４７を第５
図の矢印Ｈの方向に回転させる。このため外側偏
心カム２４も矢印Ｆの方向に回転して第５図に示
すように中心軸である後輪ハブ軸３と同心にな
る。すなわち外側偏心カム２４の偏心量がゼロの
偏心状態になる。この場合第４図においてl1＝l2
である。 Next, when the operating rod 61 is operated in the direction of the arrow E in the opposite direction, the operating plate 56 and the shaft 57 rotate in the direction of the arrow F, so that the planetary gear 58 moves to the third position.
Rotate in the direction of arrow G in the figure to move the sun gear 47 to the fifth position.
Rotate in the direction of arrow H in the figure. For this reason, the outer eccentric cam 24 also rotates in the direction of arrow F and becomes concentric with the rear wheel hub axle 3, which is the central axis, as shown in FIG. In other words, the outer eccentric cam 24 is in an eccentric state in which the amount of eccentricity is zero. In this case, l 1 = l 2 in Figure 4
It is.
したがつて第３図に示すように操作杆６１を矢
印Ａ，Ｅのように操作して、レバー５６ｂを実線
で示す位置から二点鎖線図で示す範囲の任意の位
置に操作することによつて、内側偏心カム２３と
外側偏心カム２４とによつて合成される偏心カム
の偏心量を、第４図の最大偏心状態から第５図の
偏心量ゼロの間の任意の偏心量に設定することが
できる。 Therefore, as shown in FIG. 3, by operating the operating rod 61 in the direction of arrows A and E, and moving the lever 56b from the position indicated by the solid line to any position within the range indicated by the chain double-dashed line. Therefore, the eccentricity of the eccentric cam combined by the inner eccentric cam 23 and the outer eccentric cam 24 is set to an arbitrary eccentricity between the maximum eccentricity shown in FIG. 4 and the eccentricity zero shown in FIG. be able to.
以上の変速操作は便宜上、二輪車が停止してい
る場合について説明したが、二輪車が走行中にお
いても上述した変速操作は同様に行われるから、
これによれば停止中でも走行中においても変速操
作が容易確実にできてきわめて便利である。 For convenience, the above gear shifting operation has been explained for the case where the two-wheeled vehicle is stopped, but the above gear shifting operation is performed in the same way even when the two-wheeled vehicle is running.
According to this, the gear shifting operation can be performed easily and reliably even when the vehicle is stopped or while the vehicle is running, which is extremely convenient.
第５図の偏心量ゼロの状態においては、チエン
６３によつてスプロケツト１０および駆動回転部
材１２が第７図の矢印の方向に回転すると、一
方向クラツチ３１を介して各ラチエツトリング３
２、爪３３、爪キヤリヤ３０がすべて一体的に回
転するため、この場合の駆動回転部材１２と爪キ
ヤリヤ３０との変速比は１：１となる。 In the state of zero eccentricity as shown in FIG. 5, when the sprocket 10 and drive rotating member 12 are rotated by the chain 63 in the direction of the arrow in FIG.
2. Since the pawl 33 and the pawl carrier 30 all rotate integrally, the gear ratio between the driving rotation member 12 and the pawl carrier 30 in this case is 1:1.
また操作杆６１の操作によつて合成された偏心
カムを第６図に示すように最大偏心状態にする
と、スプロケツト１０および駆動回転部材１２の
矢印方向の回転が一方向クラツチ３１を介して
ラチエツトリング３２に伝わりラチエツトリング
３２は爪３３を介して爪キヤリヤ３０に回転を伝
える。 Further, when the combined eccentric cam is brought to the maximum eccentric state by operating the operating rod 61 as shown in FIG. The rotation is transmitted to the ring 32, and the ratchet ring 32 transmits the rotation to the pawl carrier 30 via the pawl 33.
そして偏心カムが偏心している場合は、第６図
の駆動域Ｊ（この場合爪が８個あるため360゜の８
等分の角度45゜である。）内にある爪３３による増
速率が最大であるから従動回転体である爪キヤリ
ヤ３０はこの爪によつて増速回転させられ、他の
爪はラチエツトリング３２のラチエツト３２ａに
対してすべつて回転するか、または離れて回転す
ることになる。 If the eccentric cam is eccentric, drive range J in Figure 6 (in this case, there are 8 pawls, so 8 of 360 degrees)
The angle of equal division is 45°. ), the pawl carrier 30, which is a driven rotating body, is rotated at an increased speed by this pawl, and the other pawls all rotate with respect to the ratchet 32a of the ratchet ring 32. It will rotate or it will rotate away.
そして爪３３が駆動域Ｊから外れると共に、つ
ぎの爪３３が駆動域Ｊ内に入ると、今度はその爪
を介して増速駆動され、順次後続の爪へと伝動爪
が交代する。 When the pawl 33 moves out of the drive range J and the next pawl 33 enters the drive range J, it is then driven at an increased speed via that pawl, and the transmission pawl is sequentially changed to the succeeding pawl.
この場合の変速比（増速比）は、後輪ハブ軸３
の中心01を基点とする爪の駆動域である角度θ1
と、外側偏心カム２４の中心02を基点とする爪の
駆動域である角度θ2との比となる。本実施例の場
合、θ1：θ2＝１：1.4である。 In this case, the gear ratio (speed increase ratio) is the rear wheel hub axle 3.
Angle θ 1 which is the drive range of the claw with the center 0 1 as the base point
is the ratio of the angle θ 2 which is the drive range of the pawl with the center 0 2 of the outer eccentric cam 24 as the starting point. In the case of this embodiment, θ 1 :θ 2 =1:1.4.
つぎに先送りリング３９の作用について説明す
る。 Next, the function of the advance ring 39 will be explained.
すなわち、入力側の駆動回転部材１２と一体の
スプロケツト１０が第２図の矢印Ｋの方向に回転
すると、それに伴つて前述したように爪キヤリヤ
３０が増速回転する。爪キヤリヤ３０が回転する
と、これと一体のラチエツト４４も第７図の矢印
Ｌの方向に回転し、爪４１、ピン４２を介して先
送りリング３９を矢印Ｍのように増速して回転さ
せる。 That is, when the sprocket 10, which is integral with the drive rotation member 12 on the input side, rotates in the direction of arrow K in FIG. 2, the pawl carrier 30 rotates at an increased speed as described above. When the pawl carrier 30 rotates, the ratchet 44 integral therewith also rotates in the direction of arrow L in FIG. 7, causing the advance ring 39 to rotate at increased speed as shown by arrow M through the pawl 41 and pin 42.
すなわち外側偏心カム２４が偏心している場合
は、第７図の駆動域Ｎ（この場合爪が６個あるた
め360゜の６等分の角度60゜である。）にある爪によ
る増速率が最大であるから従動回転体である先送
りリング３９はこの爪によつて増速回転させら
れ、他の爪はラチエツト４４に対して矢印Ｌの方
向にすべつて回転することになる。 In other words, when the outer eccentric cam 24 is eccentric, the speed increase rate due to the pawls in the drive range N in FIG. Therefore, the advance ring 39, which is a driven rotary member, is rotated at an increased speed by this pawl, and the other pawls rotate in the direction of the arrow L with respect to the ratchet 44.
そして爪が駆動域Ｎから外れると共に、つぎの
爪が駆動域Ｎ内に入ると、今度はその爪を介して
増速駆動され、順次後続の爪へと伝動爪が交代す
る。 When the pawl moves out of the drive range N and the next pawl enters the drive range N, it is then driven at an increased speed via that pawl, and the transmission pawl is sequentially transferred to the succeeding pawl.
この場合の変速比（増速比）は、外側偏心カム
２４の中心02を基点とする爪の駆動域である角度
θ4と、後輪ハブ軸４の中心01を基点とする爪の駆
動域である角度θ3との比となる。 In this case, the speed ratio (speed increase ratio) is the angle θ 4 which is the drive range of the pawl with the center 0 2 of the outer eccentric cam 24 as the base point, and the angle θ 4 of the pawl with the center 0 1 of the rear wheel hub axle 4 as the base point. This is the ratio to the angle θ 3 which is the drive range.
すなわち先送りリング３９は増速された爪キヤ
リヤ３０よりもさらに増速されることになる。そ
して先送りリング３９はリングばね４０を介して
ラチエツトリング３２とそれぞれ摩擦接合してい
るため、爪３３のいずれか一方と噛合して伝動し
ているラチエツトリング３２はリングばね４０と
滑べつているが、遊んでいるラチエツトリング３
２はリングばね４０の摩擦接合によつてさらに増
速して先送りされる。したがつて前記した爪３３
の伝動リレー時前にたとえラチエツト３２ａと爪
３３の歯先間にギヤツプがあつても、前記した先
送りリング３９の増速回転による内歯ラチエツト
リング３２の先送りによつてラチエツト３２ａが
爪３３に直ぐ追いつくため、前記した歯先間のギ
ヤツプがなくなる。 In other words, the forwarding ring 39 is increased in speed even more than the increased speed of the pawl carrier 30. Since the advance ring 39 is frictionally connected to the ratchet ring 32 through the ring spring 40, the ratchet ring 32, which is meshing with one of the pawls 33 and transmitting power, slides on the ring spring 40. There is a ratchet ring playing with it 3
2 is further accelerated and advanced by the frictional connection of the ring spring 40. Therefore, the above-mentioned claw 33
Even if there is a gap between the tips of the teeth of the ratchet 32a and the pawl 33 before the transmission relay is activated, the ratchet 32a is moved forward to the pawl 33 by the advance of the internally toothed ratchet ring 32 due to the accelerated rotation of the advance ring 39. Since the tooth catches up immediately, the gap between the tooth tips mentioned above is eliminated.
なおラチエツト３２ａと爪３３が完全噛合して
駆動されている間は、リングばね４０が各段部３
２ｂと適度にスリツプして各部材間の速度差を吸
収することになる。 Note that while the ratchet 32a and the pawl 33 are fully engaged and driven, the ring spring 40 is applied to each step 3.
2b to absorb the speed difference between each member.
つぎに減速型芯戻し歯車機構の作用を説明す
る。第８図に示すように爪キヤリヤ３０と一体の
歯車３０ａが矢印Ｏの方向に回転すると、これと
噛合する内歯々車２７ｂを介して伝動歯車２７が
内側偏心カム２３を中心として矢印Ｏの方向に回
転するから、この伝動歯車２７の外歯々車２７ａ
と噛合する内歯々車１７ａが矢印Ｐの方向に回転
するため、この内歯々車１７ａと一体の遊星キヤ
リヤ１７も後輪ハブ軸３を中心として矢印Ｐの方
向に回転する。この場合における爪キヤリヤ３０
に対する遊星キヤリヤ１７の減速回転比は、本実
施例の場合１：0.7である。 Next, the operation of the reduction type centering gear mechanism will be explained. As shown in FIG. 8, when the gear 30a integrated with the pawl carrier 30 rotates in the direction of the arrow O, the transmission gear 27 rotates in the direction of the arrow O around the inner eccentric cam 23 via the internal gear 27b that meshes with the gear 30a. Since it rotates in the direction, the external gear 27a of this transmission gear 27
Since the internal gear wheel 17a meshing with the internal gear wheel 17a rotates in the direction of the arrow P, the planetary carrier 17 integrated with the internal gear wheel 17a also rotates in the direction of the arrow P about the rear wheel hub shaft 3. Pawl carrier 30 in this case
The reduction rotation ratio of the planetary carrier 17 to that of the planetary carrier 17 is 1:0.7 in this embodiment.
つぎ遊星歯車式増速機構の作用を説明する。前
記したように遊星キヤリヤ１７が、第９図の矢印
Ｑの方向に回転すると、軸２２を介して各遊星歯
車２１が矢印Ｑの方向に公転する。この場合駆動
回転部材１２と一体の内歯々車１５が停止してい
るとすれば、遊星歯車２１が矢印Ｒの方向に自転
する。したがつて遊星歯車２１と噛合している太
陽歯車９は、遊星歯車２１の矢印Ｑ方向の公転と
矢印Ｒ方向の自転によつて矢印Ｓの方向に増速さ
れて回転する。本実施例の場合、遊星キヤリヤ１
７に対する太陽歯車９の増速比は１：3.3である。 Next, the operation of the planetary gear speed increasing mechanism will be explained. As described above, when the planetary carrier 17 rotates in the direction of the arrow Q in FIG. 9, each planetary gear 21 revolves in the direction of the arrow Q via the shaft 22. In this case, assuming that the internal gear 15 integral with the driving rotation member 12 is stopped, the planetary gear 21 rotates in the direction of the arrow R. Therefore, the sun gear 9 meshing with the planetary gear 21 rotates at an increased speed in the direction of the arrow S due to the revolution of the planetary gear 21 in the direction of the arrow Q and the rotation in the direction of the arrow R. In this embodiment, the planetary carrier 1
The speed increasing ratio of sun gear 9 to gear 7 is 1:3.3.
そして外側偏心カム２４が最大偏心状態にあれ
ば、前述したように本実施例の場合、その爪式無
段変速機構の増速比は１：1.4であり、また減速
型芯戻し歯車機構の減速比は１：0.7であるから、
結局遊星キヤリヤ１７の回転は、1.4×0.7≒１と
なる。すなわち駆動回転部材１２と遊星キヤリヤ
１７との回転比はほぼ１：１となる。 When the outer eccentric cam 24 is in the maximum eccentric state, the speed increasing ratio of the claw type continuously variable transmission mechanism is 1:1.4 in this embodiment as described above, and the speed reduction ratio of the reduction type centering gear mechanism is 1:1.4. Since the ratio is 1:0.7,
In the end, the rotation of the planetary carrier 17 is 1.4×0.7≒1. That is, the rotation ratio between the drive rotating member 12 and the planetary carrier 17 is approximately 1:1.
したがつてこの場合、駆動回転部材１２と一体
の内歯々車１５と遊星キヤリヤ１７とが同じ回転
をすることになるため、各遊星歯車２１を介して
回転する太陽歯車９の回転も駆動回転部材１２と
同じになる。そして太陽歯車９は後輪ハブ６と一
体であるから、この場合後輪の回転数は入力であ
る駆動回転部材１２の回転数に対してほぼ１：１
となる。 Therefore, in this case, the internal gear 15, which is integral with the driving rotation member 12, and the planetary carrier 17 rotate at the same time, so the rotation of the sun gear 9, which rotates via each planetary gear 21, is also the same as the driving rotation. It becomes the same as member 12. Since the sun gear 9 is integral with the rear wheel hub 6, in this case the rotation speed of the rear wheel is approximately 1:1 with respect to the rotation speed of the drive rotating member 12 which is the input.
becomes.
また外側偏心カム２４の偏心量が前記したよう
にゼロの場合は、爪キヤリヤ３０が駆動回転部材
１２に対して１：１の回転となるため、遊星キヤ
リヤ１７の回転数は駆動回転部材１２の回転数１
に対して0.7となる。すなわちこの場合は駆動回
転部材１２に対して遊星キヤリヤ１７は比率にし
て0.3だけおくれる。しかしてこの増速機構の増
速率は3.3倍であるから、−0.3×3.3≒−１となる。
したがつてこの外側偏心カム２４の偏心量がゼロ
の場合は、１−１＝０であるから、駆動回転部材
１２と太陽歯車９との回転数の比率は、１：０と
なる。 Further, when the eccentricity of the outer eccentric cam 24 is zero as described above, the pawl carrier 30 rotates at a ratio of 1:1 with respect to the drive rotation member 12, so the rotation speed of the planetary carrier 17 is equal to that of the drive rotation member 12. Number of revolutions 1
0.7 for That is, in this case, the planetary carrier 17 is placed behind the drive rotating member 12 by a ratio of 0.3. However, since the speed increasing rate of this speed increasing mechanism is 3.3 times, -0.3 x 3.3≒-1.
Therefore, when the amount of eccentricity of the outer eccentric cam 24 is zero, since 1-1=0, the ratio of the rotational speeds of the drive rotating member 12 and the sun gear 9 is 1:0.
すなわち本実施例の無段変速装置は、１：１か
ら１：０までの広い範囲にわたつて無段変速を行
うことができる。 That is, the continuously variable transmission device of this embodiment can perform continuously variable speed over a wide range from 1:1 to 1:0.
なお遊星歯車列の増巾比を更に上げることによ
つて、マイナス回転（逆回転）を得ることも出来
る。 Note that by further increasing the width ratio of the planetary gear train, negative rotation (reverse rotation) can also be obtained.
つぎに固定部材４８と内歯々車５０との間に設
けた一方向クラツチ４９の作用を説明する。 Next, the action of the one-way clutch 49 provided between the fixing member 48 and the internal gear 50 will be explained.
無段変速装置に第２図の矢印Ｋで示す正回転方
向の駆動力が加わつた場合、二列に配置した太陽
歯車４６，４７は共に第２図の矢印Ｔの方向に回
転しようとするが、太陽歯車４６が矢印Ｔ方向に
回転すると遊星歯車５５が矢印Ｕ方向に回転し、
その結果内歯々車５０が矢印Ｖ方向に回転しなけ
ればならないが、この回転は一方向クラツチ４９
によつて阻止される。したがつて太陽歯車４６は
矢印Ｔの方向に回転することはない。また逆入力
が作用した場合は、爪キヤリヤ３０が逆方向に回
り、しかも爪キヤリヤ３０は駆動回転部材１２を
加速的に逆転増速しようとするので、駆動回転部
材１２に掛かつている負荷によつては逆転が出来
ず、装置各部に無理がかゝる。 When a driving force in the forward rotational direction shown by arrow K in FIG. 2 is applied to the continuously variable transmission, the sun gears 46 and 47 arranged in two rows both try to rotate in the direction of arrow T in FIG. , when the sun gear 46 rotates in the direction of arrow T, the planetary gear 55 rotates in the direction of arrow U,
As a result, the internal gear wheel 50 must rotate in the direction of arrow V, but this rotation is caused by the one-way clutch 49.
blocked by. Therefore, the sun gear 46 does not rotate in the direction of arrow T. Furthermore, when a reverse input is applied, the pawl carrier 30 rotates in the opposite direction, and the pawl carrier 30 attempts to accelerate the rotational drive member 12 in the reverse direction. If it does, it will not be possible to reverse the rotation and stress will be placed on each part of the device.
しかしながらこの装置では、逆入力の場合に太
陽歯車４６が第２図の矢印Ｗの方向に回転する
と、遊星歯車５５が矢印Ｘ方向に回転し、その結
果内歯々車５０が矢印Ｙの方向に回転しようとす
るが、このＹ方向の回転は一方向クラツチ４９に
よつて許容されるから問題はない。 However, in this device, when the sun gear 46 rotates in the direction of arrow W in FIG. 2 in the case of a reverse input, the planetary gear 55 rotates in the direction of arrow It tries to rotate, but this rotation in the Y direction is allowed by the one-way clutch 49, so there is no problem.
すなわち、この装置では、爪キヤリヤ３０と駆
動回転部材１２との間に無理な力が加わつた時
に、爪キヤリヤ３０と駆動回転部材１２との相対
的な位置関係を保ちながら全体として逆回転がで
きる。またこの際二列の太陽歯車４６，４７は互
いの位置関係を保ちながら逆回転するので、中心
軸に対する偏心カムの偏心量は何等変わらない。 That is, in this device, when an unreasonable force is applied between the pawl carrier 30 and the drive rotation member 12, the entire pawl carrier 30 and the drive rotation member 12 can rotate in the opposite direction while maintaining the relative positional relationship between the pawl carrier 30 and the drive rotation member 12. . Furthermore, since the two rows of sun gears 46 and 47 rotate in opposite directions while maintaining their mutual positional relationship, the amount of eccentricity of the eccentric cam with respect to the central axis does not change at all.
つまりその時の変速比を維持したまま逆入力を
許容することができる。 In other words, it is possible to allow a reverse input while maintaining the current gear ratio.
つぎに後輪ハブ６と駆動回転部材１２との間に
設けた一方向クラツチ６４の作用を説明する。 Next, the operation of the one-way clutch 64 provided between the rear wheel hub 6 and the drive rotating member 12 will be explained.
前述した爪式無段変速機構においては、スプロ
ケツト１０および駆動回転部材１２を介する入力
側の正回転（第２図の矢印Ｋ方向の回転）は、出
力側（太陽歯車９および後輪ハブ６）に伝えられ
るが、出力側からの正回転は爪３３がラチエツト
３２ａに対してすべつてしまうため伝わらない。
すなわちこの場合二輪車は惰行することになる。 In the pawl type continuously variable transmission mechanism described above, the forward rotation on the input side (rotation in the direction of arrow K in FIG. 2) via the sprocket 10 and the drive rotating member 12 is transferred to the output side (sun gear 9 and rear wheel hub 6). However, the forward rotation from the output side is not transmitted because the pawl 33 slips against the ratchet 32a.
In other words, in this case, the two-wheeled vehicle coasts.
しかしながら内燃機関を原動機とする車両にお
いては、内燃機関の回転抵抗を制動に利用する所
謂エンジンブレーキが有効に作用することが望ま
しい。 However, in a vehicle powered by an internal combustion engine, it is desirable that so-called engine braking, which utilizes the rotational resistance of the internal combustion engine for braking, be effective.
一方向クラツチ６４はこのエンジンブレーキを
作用させるために設けたもである。 A one-way clutch 64 is provided to apply this engine braking.
すなわち本装置においては、二輪車の惰行状態
における車輪の回転力が後輪ハブ６に第６図の矢
印Ｉの方向の回転として伝わると、この回転が一
方向クラツチ６４を介して駆動回転部材１２、ス
プロケツト１０、およびチエン６３等を経て内燃
機関（図示せず）に伝わることになる。したがつ
て本発明装置によれば、エンジンブレーキも有効
に利用することができる。 That is, in this device, when the rotational force of the wheels of the two-wheeled vehicle in the coasting state is transmitted to the rear wheel hub 6 as rotation in the direction of arrow I in FIG. It is transmitted to the internal combustion engine (not shown) via the sprocket 10, chain 63, etc. Therefore, according to the device of the present invention, engine braking can also be effectively utilized.
（発明の効果）
上述のように本発明においては、爪式無段変速
機構と、減速型芯戻し歯車機構と、遊星歯車式増
速機構とを中心軸回りに一体的に結合して、例え
ば二輪車の後輪のハブ内に納まるようにしたか
ら、非常に小型で、しかも入力回転数に対する出
力回転数を、例えば１：１から１：０までの広範
囲で無段変速ができるから、変速シヨツクのない
広い範囲の変速を容易に行うことができる。そし
て装置全体がハブ内に納まるため、小型軽量であ
る上に、レイアウトも非常に容易になる。(Effects of the Invention) As described above, in the present invention, the pawl type continuously variable transmission mechanism, the reduction type centering gear mechanism, and the planetary gear type speed increasing mechanism are integrally connected around the central axis, for example. Because it fits inside the hub of the rear wheel of a two-wheeled vehicle, it is extremely compact, and the output speed relative to the input speed can be continuously variable over a wide range, for example from 1:1 to 1:0, making it a variable speed shock absorber. It is possible to easily change gears over a wide range. Since the entire device is housed within the hub, it is not only small and lightweight, but also extremely easy to layout.
また本発明においては、前記爪式無段変速機構
の入力部材である駆動回転部材を外包するハブを
前記遊星歯車式増速機構の出力部材である太陽歯
車と一体的に結合し、このハブと駆動回転部材と
の間に一方向クラツチを設けたから、これによつ
てエンジンブレーキも有効に作用させることがで
きる。したがつて本発明装置は自動二輪車用変速
機としてすぐれた効果がある。 Further, in the present invention, a hub enclosing a drive rotating member which is an input member of the claw type continuously variable transmission mechanism is integrally coupled with a sun gear which is an output member of the planetary gear type speed increasing mechanism. Since a one-way clutch is provided between the drive rotating member and the rotating member, engine braking can also be effectively applied. Therefore, the device of the present invention has excellent effects as a transmission for a motorcycle.
第１図は本発明装置の縦断面図、第２図は第１
図の一部を断面で示す側面図、第３図は第１図の
−線による部分断面図、第４図は第１図の
−線による部分断面図、第５図は第４図の作動
説明図、第６図は第１図の−線による断面
図、第７図は第１図の−線による部分断面
図、第８図は第１図の−線による断面図、第
９図は第１図の−線による断面図である。
１……チエンステー、１ａ……後爪、２……バ
ツクホーク、３……後輪ハブ軸（中心軸）、６…
…後輪ハブ、９……太陽歯車、１０……スプロケ
ツト、１２……駆動回転部材、１５……内歯々
車、１７……遊星キヤリヤ、２１……遊星歯車、
２３……内側偏心カム、２４……外側偏心カム、
２７……伝動歯車、３０……爪キヤリヤ、３１…
…一方向クラツチ、３２……内歯ラチエツトリン
グ、３３……爪、３８……ローラ、３９……先送
りリング、４０……リングばね、４１……爪、４
４……ラチエツト、４５……長穴、４６，４７…
…太陽歯車、４８……固定部材、４９……一方向
クラツチ、５０……内歯々車、５４……軸、５５
……遊星歯車、５６……操作プレート、６１……
操作杆、６３……チエン、６４……一方向クラツ
チ。
FIG. 1 is a longitudinal sectional view of the device of the present invention, and FIG.
3 is a partial sectional view taken along the - line in FIG. 1; FIG. 4 is a partial sectional view taken along the - line in FIG. 1; FIG. Explanatory drawings, FIG. 6 is a sectional view taken along the - line in FIG. 1, FIG. 7 is a partial sectional view taken along the - line in FIG. 1, FIG. 8 is a sectional view taken along the - line in FIG. 1, and FIG. FIG. 2 is a sectional view taken along the - line in FIG. 1; 1... Chain stay, 1a... Rear claw, 2... Back hawk, 3... Rear wheel hub shaft (center shaft), 6...
... Rear wheel hub, 9 ... Sun gear, 10 ... Sprocket, 12 ... Drive rotation member, 15 ... Internal toothed wheel, 17 ... Planetary carrier, 21 ... Planetary gear,
23...Inner eccentric cam, 24...Outer eccentric cam,
27... Transmission gear, 30... Pawl carrier, 31...
...One-way clutch, 32... Internal tooth ratchet ring, 33... Pawl, 38... Roller, 39... Advance ring, 40... Ring spring, 41... Pawl, 4
4... Ratchet, 45... Long hole, 46, 47...
... Sun gear, 48 ... Fixed member, 49 ... One-way clutch, 50 ... Internal gear wheel, 54 ... Shaft, 55
... Planetary gear, 56 ... Operation plate, 61 ...
Operation lever, 63...chain, 64...one-way clutch.
Claims (1)
より偏心量を調整自在にした偏心カムを中心軸に
設け、この偏心カムを外包するように中空円筒状
に形成した入力側の駆動回転部材の内周に内歯ラ
チエツトを設け、この内歯ラチエツトに噛合する
爪の基部を前記偏心カムに回転自在に設けた爪キ
ヤリヤに枢支し、この爪キヤリヤの外周に設けた
歯車を前記内側偏心カムに設けた伝動歯車を介し
て前記中心軸に設けた遊星キヤリヤの内歯々車と
噛合し、この遊星キヤリヤに設けた遊星歯車を前
記駆動回転部材に設けた内歯々車に噛合すると共
に出力側の太陽歯車に噛合し、前記駆動回転部材
を外包するハブを前記太陽歯車と一体的に結合
し、このハブと駆動回転部材との間に一方向クラ
ツチを設けたことを特徴とする二輪車用無段変速
装置。1. An eccentric cam whose eccentricity can be freely adjusted by a combination of an inner eccentric cam and an outer eccentric cam is provided on the central shaft, and the inner periphery of the drive rotating member on the input side is formed into a hollow cylindrical shape so as to enclose this eccentric cam. an internal toothed ratchet is provided on the inside toothed ratchet, the base of a pawl that meshes with this internal toothed ratchet is pivotally supported on a pawl carrier rotatably provided on the eccentric cam, and a gear provided on the outer periphery of the pawl carrier is provided on the inner eccentric cam. The transmission gear meshes with the internal toothed wheel of the planetary carrier provided on the central shaft, and the planetary gear provided on the planetary carrier meshes with the internal toothed wheel provided on the drive rotating member, and the output side A stepless clutch for a two-wheeled vehicle, characterized in that a hub meshing with a sun gear and enclosing the drive rotation member is integrally coupled with the sun gear, and a one-way clutch is provided between the hub and the drive rotation member. gearbox.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61164703A JPS6323050A (en) | 1986-07-15 | 1986-07-15 | Continuously variable transmission for motor cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61164703A JPS6323050A (en) | 1986-07-15 | 1986-07-15 | Continuously variable transmission for motor cycle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6323050A JPS6323050A (en) | 1988-01-30 |
| JPH0150783B2 true JPH0150783B2 (en) | 1989-10-31 |
Family
ID=15798267
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61164703A Granted JPS6323050A (en) | 1986-07-15 | 1986-07-15 | Continuously variable transmission for motor cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6323050A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103335074B (en) * | 2013-06-13 | 2017-02-08 | 王俊生 | Planetary gear continuously variable transmission with eccentric type planetary gear |
| JP6245363B2 (en) * | 2014-06-24 | 2017-12-13 | 京セラドキュメントソリューションズ株式会社 | ADJUSTMENT MECHANISM, IMAGE FORMING DEVICE HAVING ADJUSTMENT MECHANISM, AND ADJUSTMENT METHOD USING ADJUSTMENT MECHANISM |
| CN106627975B (en) * | 2017-01-20 | 2021-12-17 | 张家港川梭车业有限公司 | Single-wheel direct-drive transmission is trampled to straight line |
| CN110645325A (en) * | 2018-06-27 | 2020-01-03 | 重庆交通大学 | Manual single-row planetary gear transmission |
-
1986
- 1986-07-15 JP JP61164703A patent/JPS6323050A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6323050A (en) | 1988-01-30 |
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