JPS63130956A - Continuously variable transmission - Google Patents
Continuously variable transmissionInfo
- Publication number
- JPS63130956A JPS63130956A JP27292186A JP27292186A JPS63130956A JP S63130956 A JPS63130956 A JP S63130956A JP 27292186 A JP27292186 A JP 27292186A JP 27292186 A JP27292186 A JP 27292186A JP S63130956 A JPS63130956 A JP S63130956A
- Authority
- JP
- Japan
- Prior art keywords
- friction wheel
- input shaft
- driven
- driving
- eccentric cam
- 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 39
- 230000003321 amplification Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Landscapes
- Friction Gearing (AREA)
- Transmission Devices (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、産業機械および搬送機器等に装備するのに適
した汎用の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 general-purpose continuously variable transmission device suitable for equipping industrial machinery, conveyance equipment, and the like.
（従来の技術）
有段の変速装置は、その段階的変速時にショックが発生
し、また常に最適な出力回転が得られないという問題点
が・ある。(Prior Art) Stepped transmissions have problems in that shocks occur during stepwise shifting, and optimum output rotation cannot always be obtained.
無段変速装置は、このような問題点を解消するものであ
るが、従来の機械式無段変速装置としては、摩擦車式無
段変速機が多く実用化されている。Continuously variable transmissions are intended to solve these problems, but many conventional mechanical continuously variable transmissions include friction wheel type continuously variable transmissions.
−例としてあげれは実公昭４９−２９１６８号公報に開
示されたものがある。- An example is the one disclosed in Japanese Utility Model Publication No. 49-29168.
（発明が解決しようとする問題点）
上述した従来の摩擦車式無段変速装置は、主に円錐車の
摩擦伝動接点の回転半径を無段階に変えることによって
無段の変速伝動を行うものである。(Problems to be Solved by the Invention) The conventional friction wheel type continuously variable transmission described above performs continuously variable speed transmission mainly by continuously changing the rotation radius of the friction transmission contacts of the conical wheel. be.
しかしながら円錐車の摩擦伝動接点は、ヘルツ応力によ
ってそのピッチラインに相当する接触軌道が帯状となる
から、その接触軌道上の径の大きい側と小さい側におい
て、一方に正、一方に負のすべりを発生する結果、これ
が内部摩擦損失となって伝動効率を低下させるという問
題点がある。また変速比が最高、最低の時は、駆動摩擦
車および従動摩擦車に対する摩擦伝動接点のピッチライ
ン径の比が１：２〜１：４というように大きくなるため
、前記した正、負のすべりが急増し、いわゆるトップや
ローの伝動時において伝動効率が著しく低下するという
問題点があった。However, in the friction transmission contact of a conical wheel, the contact trajectory corresponding to the pitch line becomes band-shaped due to Hertzian stress, so one side of the contact trajectory has a positive slip and the other has a negative slip on the large diameter side and the small diameter side. As a result, there is a problem in that this causes internal friction loss and reduces transmission efficiency. Furthermore, when the gear ratio is the highest or lowest, the ratio of the pitch line diameter of the friction transmission contact to the driving friction wheel and the driven friction wheel becomes large, such as 1:2 to 1:4, so that the above-mentioned positive and negative slips occur. There has been a problem in that the transmission efficiency has sharply decreased during so-called top and low transmission.
（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、入力軸
に対して偏心量調整自在にした駆動摩擦車を回転自在に
設け、この駆動摩擦車と同心の内歯歯車をこの駆動摩擦
車と一体的に形成し、前記入力軸と同心の２個の内歯歯
車をこの入力軸と一体的に形成し、この一方の内歯歯車
と前記駆動摩擦車と一体の内歯歯車を中間伝動歯車を介
して噛合連結し、前記入力軸を中心にして中空円筒状の
従動回転体を回転自在に設けると共に、この従動回転体
の内周に従動回転体と共に回転する従動摩擦車を設け、
この従動摩擦車と前記駆動摩擦車とを圧接係合させ、前
記従動回転体に遊星キャリヤを一体的に設け、この遊星
キャリヤに枢支した遊星歯車を前記入力軸と一体の他方
の内歯歯車に噛合させると共に、前記入力軸と同心の出
力軸と一体の太陽歯車に噛合させて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, a drive friction wheel whose eccentricity can be freely adjusted with respect to the input shaft is rotatably provided, and a drive friction wheel concentric with the drive friction wheel is provided. An internal gear is integrally formed with the drive friction wheel, two internal gears coaxial with the input shaft are integrally formed with the input shaft, and one of the internal gears and the drive friction wheel are formed integrally with the input shaft. An integral internal gear is meshed and connected via an intermediate transmission gear, and a hollow cylindrical driven rotary body is rotatably provided around the input shaft, and the inner circumference of the driven rotary body rotates together with the driven rotary body. A driven friction wheel is provided to
The driven friction wheel and the driving friction wheel are press-fitted, a planetary carrier is integrally provided on the driven rotating body, and the planetary gear pivotally supported on the planetary carrier is connected to the other internal gear integral with the input shaft. A continuously variable transmission is constructed by meshing with a sun gear integral with the output shaft, which is concentric with the input shaft.
（作 用）
上述のように本発明装置は摩擦伝動用に円錐車を使用せ
ず、入力軸に対して偏心量調整自在にした駆動摩擦車と
、従動回転体と共に回転する従動摩擦車とを圧接係合に
よって直接接触するようにし、特にトップの変速状態に
おいては駆動摩擦車と従動摩擦車が同心状態で接合する
ようにしたから、この場合側摩擦車は全周において圧接
接合する結果、すべりのない１００％近くの極めて高い
伝動効率を得ることができる。(Function) As described above, the device of the present invention does not use a conical wheel for friction transmission, but uses a driving friction wheel whose eccentricity can be freely adjusted with respect to the input shaft, and a driven friction wheel that rotates together with the driven rotating body. Direct contact is achieved by pressure welding engagement, and the driving friction wheel and driven friction wheel are concentrically connected, especially in the top gear shifting state.In this case, the side friction wheels are pressure welded all around the circumference, resulting in no slippage. An extremely high transmission efficiency of nearly 100% can be obtained.
また従動摩擦車に対して駆動摩擦車が偏心して両摩擦車
が部分的に接合するトップ以外の変速状態になっても両
摩擦車における摩擦伝動接点のピッチライン径の比はｌ
：２より近接したものとなるから、摩擦伝動接触線が前
記のピッチライン上にかなり長く形成されると共に、ピ
ッチラインの両側に存在する正、負のすべり帯域も従来
のものより狭くなる結果、トップ以外の変速域において
もかなり高い伝動効率を得ることができる。In addition, even if the driving friction wheel is eccentric with respect to the driven friction wheel and the shifting state is other than the top where both friction wheels are partially connected, the ratio of the pitch line diameters of the friction transmission contacts of both friction wheels is l.
: 2, the friction transmission contact line is formed considerably longer on the pitch line, and the positive and negative slip zones on both sides of the pitch line are also narrower than in the conventional one. Considerably high transmission efficiency can be achieved even in shift ranges other than the top.
（実施例）
以下、第１図〜第８図について本発明の一実施例を説明
する。(Example) Hereinafter, an example of the present invention will be described with reference to FIGS. 1 to 8.
図中１は中空円筒状のケース本体、２はケース本体１と
一体に形成したベース、３はケース本体１の入力側にボ
ルト４により接続した入力側ケース蓋、５はケース本体
１の出力側にボルト４により接続した出力側ケース蓋、
６はケース本体ｌの上部に設けたオイルキャップ、７は
ケース本体ｌの底部に設けた排油栓である。In the figure, 1 is a hollow cylindrical case body, 2 is a base formed integrally with the case body 1, 3 is an input side case lid connected to the input side of the case body 1 with a bolt 4, and 5 is the output side of the case body 1. output side case lid connected by bolt 4 to
6 is an oil cap provided at the top of the case body l, and 7 is an oil drain plug provided at the bottom of the case body l.
本実施例においては、出力側ケース蓋５のボス部５ａを
貫通する出力軸８を軸受９，１０を介して回転自在に設
け、この出力軸８の内側端部には円形凹陥部８ａを設け
ると共に、その外周部に太陽歯車１１を出力軸８と一体
に形成する。１２はボス部５ａの外側にボルト１３によ
り取り付けた軸受押え、１４はその内周部に設けたラビ
リンスである。In this embodiment, an output shaft 8 passing through the boss portion 5a of the output case lid 5 is rotatably provided via bearings 9 and 10, and a circular recess 8a is provided at the inner end of the output shaft 8. At the same time, a sun gear 11 is integrally formed with the output shaft 8 on its outer circumference. Reference numeral 12 denotes a bearing retainer attached to the outside of the boss portion 5a with bolts 13, and reference numeral 14 denotes a labyrinth provided on the inner circumference thereof.
また出力軸８と同心の入力軸１５を入力側ケース蓋３を
貫通すると共に、その内側端部を出力軸８の円形凹陥部
８ａ内に軸受１６を介して回転自在に挿入する。１７は
入力軸１５がケース蓋３を貫通する部分に設けた軸受、
１８はボルト１９．２０によりケース蓋３に取り付けた
軸受押え、１４はその内周部に設けたラビリンスである
。An input shaft 15 coaxial with the output shaft 8 passes through the input case lid 3, and its inner end is rotatably inserted into the circular recess 8a of the output shaft 8 via a bearing 16. 17 is a bearing provided at the part where the input shaft 15 passes through the case lid 3;
18 is a bearing holder attached to the case lid 3 with bolts 19 and 20, and 14 is a labyrinth provided on its inner circumference.
また入力軸１５と同心の２個の内歯歯車２１．２２を背
中合わせにしてボルト２３により結合すると共に、この
結合体をボルト２４およびキー２５を介して入力軸１５
に固着する。Further, two internal gears 21 and 22 concentric with the input shaft 15 are connected back to back with a bolt 23, and this combined body is connected to the input shaft 15 through a bolt 24 and a key 25.
sticks to.
また第４図および第５図に示すように、入力軸１５の中
心０１に対してＩ２１だけ偏心した内側偏心カム２６を
入力軸１５に対して回転自在に嵌装すると共に、その外
側端部を第１図に示すようにケース蓋３内に嵌入してボ
ルト２０により固定する。２７は入力軸１５と内側偏心
カム２６との間に介装した軸受である。Further, as shown in FIGS. 4 and 5, an inner eccentric cam 26 that is eccentric by I21 with respect to the center 01 of the input shaft 15 is rotatably fitted to the input shaft 15, and its outer end is As shown in FIG. 1, it is fitted into the case lid 3 and fixed with bolts 20. 27 is a bearing interposed between the input shaft 15 and the inner eccentric cam 26.
また第４図および第５図に示すように、内側偏心カム２
６の中心０２に対して１２だけ偏心した外側偏心カム２
８を内側偏心カム２６に対して回転自在に嵌装する。な
お、この場合１．＝１２とする。In addition, as shown in FIGS. 4 and 5, the inner eccentric cam 2
The outer eccentric cam 2 is eccentric by 12 with respect to the center 02 of 6.
8 is rotatably fitted to the inner eccentric cam 26. In this case, 1. =12.
また外側偏心カム２８の入力端に中空円筒部２９を一体
に形成し、この中空円筒部２９の入力端端面に、内側偏
心カム２６を中心軸とするウオームホイール３０をボル
ト３１により固定して設け、このウオームホイール３０
と噛合するウオーム３２と一体の軸３２ａを、第２図に
示すようにケース蓋３に対して回転自在に設ける。３３
はブツシュ、３４は円筒状の止めねじ、３５はロックナ
ツト、３６は軸３２ａに固着したハンドルである。Further, a hollow cylindrical portion 29 is integrally formed at the input end of the outer eccentric cam 28 , and a worm wheel 30 having the inner eccentric cam 26 as its central axis is fixed to the input end face of the hollow cylindrical portion 29 with bolts 31 . , this worm wheel 30
A shaft 32a integral with the worm 32 that engages with the case lid 3 is rotatably provided with respect to the case lid 3, as shown in FIG. 33
34 is a cylindrical set screw, 35 is a lock nut, and 36 is a handle fixed to the shaft 32a.
また外側偏心カム２８の外周に中空円筒状の駆動回転体
３７を軸受３８を介して回転自在に設け、この駆動回転
体３７の胴部中央に■プーリ状の駆動摩擦車３９を駆動
回転体３７と一体に設け、さらに駆動回転体３７の出力
側端面に、前記内歯歯車２２と同様の内歯歯車４０を駆
動回転体３７と同心にしてボルト４１により固定して設
ける。なお４２は外側偏心カム２８の出力側端面にビス
４３によって固定した軸受押え板である。Further, a hollow cylindrical driving rotary body 37 is rotatably provided on the outer periphery of the outer eccentric cam 28 via a bearing 38, and a pulley-shaped driving friction wheel 39 is installed in the center of the body of the driving rotary body 37. Further, an internal gear 40 similar to the internal gear 22 is provided on the output side end face of the drive rotary body 37 and fixed with a bolt 41 concentrically with the drive rotary body 37. Note that 42 is a bearing holding plate fixed to the output side end surface of the outer eccentric cam 28 with screws 43.
また第１図、第６図および第７図に示すように、外側偏
心カム２８が内側偏心カム２６の回りに回動しても、常
に内歯歯車４０と噛合すると共に、内歯歯車２２とも噛
合する中間伝動歯車４４を軸受４５を介して内側偏心カ
ム２６に回転自在に設ける。４６はワッシャ、４７はカ
ラーである。Further, as shown in FIGS. 1, 6, and 7, even when the outer eccentric cam 28 rotates around the inner eccentric cam 26, it always meshes with the internal gear 40 and also engages with the internal gear 22. An intermeshed intermediate transmission gear 44 is rotatably provided on the inner eccentric cam 26 via a bearing 45. 46 is a washer, and 47 is a collar.
また中空円筒状の胴部４８ａと、入力端フランジ部４８
ｂと、出力側フランジ部４８Ｃとを、それぞれボルト４
９により一体に結合した従動回転体４８を、入力軸１５
および出力軸８を中心にしてケース本体１内に軸受５０
．５１を介して回転自在に設け、この従動回転体４８の
胴ｆｉ４８ａの内周に従動摩擦車５２を従動回転体４８
と共に回転するように設ける。５３は従動回転体４８と
従動摩擦車５２との間に設けたすべりキーである。従動
摩擦車５２は２個のリング部材５２ａを対向させると共
に、その間に複数個（本実施例では４個）のばね５４を
介挿して構成されている。In addition, a hollow cylindrical body portion 48a and an input end flange portion 48
b and output side flange portion 48C with bolts 4, respectively.
The input shaft 15 connects the driven rotating body 48 integrally by
and a bearing 50 inside the case body 1 around the output shaft 8.
．． 51, and the driven friction wheel 52 is connected to the inner circumference of the body fi48a of the driven rotary body 48.
provided so that it rotates with the 53 is a sliding key provided between the driven rotating body 48 and the driven friction wheel 52. The driven friction wheel 52 includes two ring members 52a facing each other and a plurality of (four in this embodiment) springs 54 interposed therebetween.
また第１図および第８図に示すように、従動回転体４８
の出力側フランジ部４８Ｃの内側に遊星キャリヤ５５を
ボルト５６（第８図参照）により固定し、この遊星キャ
リヤ５５に複数個（本実施例では４個）の遊星歯車５７
を軸５８および軸受５９により回転自在に設け、これら
の遊星歯車５７を前記内歯歯車２１に内接噛合させると
共に、出力軸８と一体の太陽歯車１１にそれぞれ外接噛
合させる。なお６０は内歯歯車２１のボス部と遊星キャ
リヤ５５との間に設けただ軸受である。Further, as shown in FIGS. 1 and 8, the driven rotating body 48
A planetary carrier 55 is fixed to the inside of the output side flange portion 48C with bolts 56 (see FIG. 8), and a plurality of (four in this embodiment) planetary gears 57 are fixed to the planetary carrier 55.
are rotatably provided by a shaft 58 and a bearing 59, and these planetary gears 57 are internally meshed with the internal gear 21 and externally meshed with the sun gear 11, which is integrated with the output shaft 8. Note that 60 is a bearing provided between the boss portion of the internal gear 21 and the planetary carrier 55.
また第９図は本発明の変形例を示すもので、図中前記実
施例と同一の符号は同等のものを示す。FIG. 9 shows a modified example of the present invention, and the same reference numerals as in the embodiment described above indicate equivalent parts.
これは駆動摩擦車と従動摩擦車とを前記実施例と逆にし
たものである。In this embodiment, the driving friction wheel and the driven friction wheel are reversed from those of the previous embodiment.
すなわちこの場合は、断面形状が楔状のものをリング状
に形成した従動摩擦車６１を従動回転体４８に固着し、
駆動摩擦車６２は、駆動回転体３７を外包すると共に、
この駆動回転体３７に対してキー６３により軸方向に摺
動自在に設けた２個のリング６２ａをそれぞれ従動摩擦
車６１を挟圧するように配置して構成する。６４はリン
グ６２ａを従動摩擦車６１に押し付けるためのコイルば
ねである。That is, in this case, a driven friction wheel 61 having a wedge-shaped cross section formed into a ring shape is fixed to the driven rotating body 48,
The driving friction wheel 62 encloses the driving rotating body 37, and
Two rings 62a are provided slidably in the axial direction with a key 63 with respect to the driving rotary body 37, and are arranged so as to press the driven friction wheel 61, respectively. 64 is a coil spring for pressing the ring 62a against the driven friction wheel 61.
つぎに上述のように構成した本発明装置の作用を、まず
第１図〜第８図の実施例について説明する。第２図にお
いてハンドル３６を回転させると、ウオーム３２、ウオ
ームホイール３０を介して外側偏心カム２８がケース蓋
３に固定した内側偏心カム２６に対して回動するため、
入力軸１５および出力軸８に対する外側偏心カム２８の
偏心量を自由に変化させることができる。第１．４．６
図は外側偏心カム２８の入力軸１５に対する偏心量がゼ
ロの場合を示すもので、この状態では駆動摩擦車３９と
従動摩擦車５２とが同心になるため、両摩擦車３９．５
２は全周において接触し、しかも従動摩擦車５２の両側
のリング部材５２ａがばね５４の作用により■プーリ状
の駆動摩擦車３９の溝の両側壁面に圧接しているため、
駆動摩擦車３９が回転すれば従動摩擦車５２もほとんど
すべることなく一体的に回転する。Next, the operation of the apparatus of the present invention constructed as described above will be explained first with reference to the embodiments shown in FIGS. 1 to 8. In FIG. 2, when the handle 36 is rotated, the outer eccentric cam 28 rotates relative to the inner eccentric cam 26 fixed to the case lid 3 via the worm 32 and the worm wheel 30.
The amount of eccentricity of the outer eccentric cam 28 with respect to the input shaft 15 and the output shaft 8 can be freely changed. Section 1.4.6
The figure shows a case where the amount of eccentricity of the outer eccentric cam 28 with respect to the input shaft 15 is zero. In this state, the driving friction wheel 39 and the driven friction wheel 52 are concentric, so both friction wheels 39.5
2 are in contact with each other around the entire circumference, and the ring members 52a on both sides of the driven friction wheel 52 are in pressure contact with both side wall surfaces of the groove of the pulley-shaped driving friction wheel 39 due to the action of the spring 54.
When the driving friction wheel 39 rotates, the driven friction wheel 52 also rotates integrally with almost no slippage.
したがってこの状態で入力軸１５が第４図の矢印への方
向に回転ずれば、入力軸１５と一体の内歯歯車２１．２
２が第６図の矢印Ｂの方向に回転し、内歯歯車２２と噛
合する中間伝動歯車４４、およびこの中間伝動歯車４４
と噛合する内歯歯車４０を介して、この内歯歯車４０と
一体的に結合した駆動摩擦車３９も第４図の矢印Ｃの方
向に入力軸１５と一体的に回転する。しかして上述した
ように駆動摩擦車３９が回転すれば、従動摩擦車５２も
第４図の矢印りの方向に入力軸１５と一体的に回転する
。また従動摩擦車５２とキー５３とを介して連結した従
動回転体４８も入力軸１５と共に回転するから、この従
動回転体４８と一体的に結合した遊星ヰ゛ヤリャ５５を
介して、各遊星歯車５７も、内歯歯車２１が入力軸１５
と一体的に回転しているから入力軸１５と一体的に公転
する。その結果、第８図に示すように、これらの遊星歯
車５７と噛合する太陽歯車１１も出力軸８と共に、入力
軸１５と一体的に回転する。すなわちこの場合の入力軸
１５０回転と、出力軸８の回転比はｌ：１である。この
状態が本無段変速装置の所謂トップの変速状態である。Therefore, if the input shaft 15 rotates in the direction of the arrow in FIG. 4 in this state, the internal gear 21.2 integral with the input shaft 15
2 rotates in the direction of arrow B in FIG. 6 and meshes with the internal gear 22, and this intermediate transmission gear 44.
The drive friction wheel 39, which is integrally connected to the internal gear 40, also rotates integrally with the input shaft 15 in the direction of arrow C in FIG. 4. When the driving friction wheel 39 rotates as described above, the driven friction wheel 52 also rotates integrally with the input shaft 15 in the direction of the arrow in FIG. Further, since the driven rotating body 48 connected via the driven friction wheel 52 and the key 53 also rotates together with the input shaft 15, each planetary gear 57 also rotates through the planetary gear 55 integrally connected to the driven rotating body 48. , the internal gear 21 is the input shaft 15
Since it rotates integrally with the input shaft 15, it revolves integrally with the input shaft 15. As a result, as shown in FIG. 8, the sun gear 11 meshing with these planetary gears 57 also rotates together with the output shaft 8 and the input shaft 15. That is, in this case, the rotation ratio between the input shaft 150 rotations and the output shaft 8 is 1:1. This state is the so-called top shift state of the continuously variable transmission.
つぎにこのトップの変速状態より第２図のハンドル３６
を操作して外側偏心カム２８を約１８０°回動させると
、外側偏心カム２８が第３，５図の最大偏心状態になる
から、それに伴って駆動摩擦車３９も第３．５図に示す
ように従動摩擦車５２に対して偏心する。このため駆動
摩擦車３９と従動摩擦車５２との接触部は、第３．５図
に示すＥ点付近のみになる。そしてこの状態で入力軸１
５を介して駆動摩擦車３９が第５図の矢印Ｆの方向に回
転すると、従動摩擦車５２も矢印Ｇの方向に回転するが
、この場合両摩擦車３９．５２の摩擦伝動点Ｅまでの回
転半径に差が生ずる。すなわち第５図において入力軸１
５および従動摩擦車５２の中心を０．とし、駆動摩擦車
３９の中心を０３とし、０３からＥ点までの半径をＲ，
とし、０、からＥ点までの半径をＲ２とすると、Ｒ，＜
Ｒ２となる。このためこの場合は、駆動摩擦車３９に対
して従動摩擦車５２は減速されて回転することになる。Next, from the top speed change state, the handle 36 in Fig. 2
When the outer eccentric cam 28 is rotated approximately 180 degrees by operating the outer eccentric cam 28, the outer eccentric cam 28 becomes the maximum eccentric state shown in Figs. Thus, it is eccentric with respect to the driven friction wheel 52. Therefore, the contact portion between the driving friction wheel 39 and the driven friction wheel 52 is only near point E shown in FIG. 3.5. In this state, input shaft 1
5, when the driving friction wheel 39 rotates in the direction of arrow F in FIG. 5, the driven friction wheel 52 also rotates in the direction of arrow G. There will be a difference in the turning radius. In other words, in Fig. 5, input shaft 1
5 and the center of the driven friction wheel 52 to 0. The center of the driving friction wheel 39 is 03, and the radius from 03 to point E is R,
If the radius from 0 to point E is R2, then R,<
It becomes R2. Therefore, in this case, the driven friction wheel 52 rotates at a reduced speed with respect to the driving friction wheel 39.
本実施例の場合その減速比は１：０．６７程度である。In this embodiment, the reduction ratio is approximately 1:0.67.
すなわち入力軸１５の回転１に対して０．３３だけ減速
することになる。That is, the rotation speed of the input shaft 15 is reduced by 0.33 per rotation.
そして従動摩擦車５２が減速回転すると、キー５３およ
び従動回転体４８を介して、この従動回転体４８と一体
の遊星キャリヤ５５が第８図の矢印Ｈの方向に回転する
。他方遊星キャリヤ５５より外側の内歯歯車２１は、入
力軸１５にキー２５を介して固定されているから、第８
図の矢印Ｉで示すように遊星キャリヤ５５より速い速度
で同方向に回転する。このため各遊星歯車５７は、第８
図において矢印Ｈのように公転すると共に、矢印Ｊの方
向に自転するから、これらの遊星歯車５７と噛合する太
陽歯車１１はさらに減速されることになる。すなわちこ
の遊星歯車装置は、従動摩擦車５２の減速をさらに増幅
する。When the driven friction wheel 52 rotates at a reduced speed, the planetary carrier 55, which is integral with the driven rotary body 48, rotates in the direction of arrow H in FIG. 8 via the key 53 and the driven rotary body 48. On the other hand, the internal gear 21 on the outside of the planetary carrier 55 is fixed to the input shaft 15 via the key 25.
As shown by arrow I in the figure, it rotates in the same direction at a faster speed than the planetary carrier 55. Therefore, each planetary gear 57 has an eighth
Since it revolves in the direction of arrow H and rotates on its own axis in the direction of arrow J in the figure, the sun gear 11 meshing with these planetary gears 57 is further decelerated. That is, this planetary gear device further amplifies the deceleration of the driven friction wheel 52.
本実施例における増幅倍数は約３であるから、最低の変
速状態（ロー）における出ツノ軸８０回転は、前記摩擦
伝動部の減速率０．３３の３倍、すなわち−０，３３Ｘ
３ζ−１で、１−１＝０であるから略ゼロになる。Since the amplification factor in this embodiment is approximately 3, the output horn shaft 80 rotations in the lowest speed change state (low) is 3 times the deceleration rate of 0.33 of the friction transmission section, that is, -0.33X
Since 3ζ-1 and 1-1=0, it becomes approximately zero.
そして第２図のハンドル３６の操作量を前記したトップ
とローとの中間の任意の操作量とすれば、ローからトッ
プまでの間で無段の変速比が得られることになる。If the operating amount of the handle 36 in FIG. 2 is set to an arbitrary operating amount between the above-mentioned top and low, a stepless gear ratio will be obtained from low to top.
なお本装置は必要があれば、前記した減速率または増幅
倍数を大きくすることによって、入力軸に対して出力軸
を逆回転させることもできる。Note that, if necessary, this device can also rotate the output shaft in the opposite direction with respect to the input shaft by increasing the deceleration rate or amplification factor described above.
また第９図に示す変形例の場合も作用は前記実施例と同
様であるから説明は省略する。Also, in the case of the modified example shown in FIG. 9, the operation is similar to that of the previous embodiment, so the explanation will be omitted.
（発明の効果）
上述のように本発明装置は摩擦伝動用に円錐車を使用せ
ず、入力軸１５に対して偏心量調整自在にした駆動摩擦
車３９と、従動回転体４８と共に回転する従動摩擦車５
２とを圧接係合によって直接接触するようにし、特にト
ップの変速状態においては駆動摩擦車３９と従動摩擦車
５２が同心状態で接合するようにしたから、この場合両
摩擦車３９．５２は全周において圧接接合する結果、す
べりのない１００％近くの極めて高い伝動効率を得るこ
とができる。(Effects of the Invention) As described above, the device of the present invention does not use a conical wheel for friction transmission, but uses a drive friction wheel 39 whose eccentricity can be freely adjusted with respect to the input shaft 15, and a follower that rotates together with the driven rotor 48. dynamic friction wheel 5
2 are brought into direct contact by press-fitting engagement, and the driving friction wheel 39 and the driven friction wheel 52 are concentrically connected, especially in the top gear shifting state. As a result of pressure welding at the periphery, extremely high transmission efficiency of nearly 100% with no slippage can be obtained.
また従動摩擦車５２に対して駆動摩擦車３９が偏心して
、両摩擦車が部分的に接合゛するトップ以外の変速状態
になっても、両摩擦車における摩擦伝動接点Ｅのピッチ
ライン径の比はｌ：２より近接したものとなるから、摩
擦伝動接触線が前記のピッチライン上にかなり長く形成
されると共に、ピッチラインの両側に存在する正、負の
すべり帯域も従来のものより狭くなる結果、トップ以外
の変速域においてもかなり高い伝動効率を得ることがで
きる。Furthermore, even if the drive friction wheel 39 is eccentric with respect to the driven friction wheel 52 and the transmission state is other than the top where both friction wheels are partially connected, the ratio of the pitch line diameters of the friction transmission contacts E of both friction wheels is closer than l:2, so the friction transmission contact line is formed quite long on the pitch line, and the positive and negative slip bands on both sides of the pitch line are also narrower than in the conventional one. As a result, considerably high transmission efficiency can be achieved even in shift ranges other than the top.
特に本発明においては、ケース本体１の中心に位置する
入力軸１５側に偏心カム機構を設けたから、偏心カム機
構をケース側に設けたものと比較した場合、駆動摩擦車
３９と従動摩擦車５２との係合接点の回転半径を大きく
することができる。このため本発明は伝動トルクを大き
くすることができる。In particular, in the present invention, since the eccentric cam mechanism is provided on the input shaft 15 side located at the center of the case body 1, when compared with a case where the eccentric cam mechanism is provided on the case side, the driving friction wheel 39 and the driven friction wheel 52 It is possible to increase the rotation radius of the engagement contact point with the Therefore, the present invention can increase the transmission torque.
したがって本発明によれば、構造が比較的簡単で、変速
幅が大きく、伝動トルクも大きい上に、特にトップ状態
での伝動効率が極めて高い無段変速装置を比較的安価に
提供することができるという効果が得られる。Therefore, according to the present invention, it is possible to provide, at a relatively low cost, a continuously variable transmission device that has a relatively simple structure, a wide shift width, a large transmission torque, and has extremely high transmission efficiency, especially in the top state. This effect can be obtained.
第１図は本発明装置の縦断側面図、
第２図はその一部を第１図のＩＩ−ＩＩ断面で示す入力
軸側より見た正面図、
第３図は第１図の偏心カムが偏心した状態を一部断面で
示す側面図、
第４図は第１図のｒＶ−ｒＶ断面図、
第５図は第３図のＶ−■断面図、
第６図は第１図のＶＩ−Ｖｌ断面図、
第７図は第３図の■−■断面図、
第８図は第１図の■−■断面図、
第９図は本発明装置の変形例を一部断面で示す側面図で
ある。
■・・・ケース本体 ２・・・ベース３・・・入
力側ケース蓋 ５・・・出力側ケース蓋８・・・出力
軸 １１・・・太陽歯車１５・・・入力軸
２１．２２・・・内歯歯車２６・・・内側偏
心カム ２８・・・外側偏心カム３０・・・ウオー
ムホイール ３２・・・ウオーム３６・・・ハンドル
３７・・・駆動回転体３９・・・駆動摩擦車
４０・・・内歯歯車４４・・・中間伝動歯車
４８・・・従動回転体５２・・・従動摩擦車
５４・・・ばね５５・・・遊星キャリヤ ５７・・
・遊星歯車特許出願人 ブリデストンサイクル株式
会社第４図Fig. 1 is a longitudinal sectional side view of the device of the present invention, Fig. 2 is a front view of a part of the device taken along the line II-II in Fig. 1 as seen from the input shaft side, and Fig. 3 shows the eccentric cam of Fig. 1. 4 is a sectional view along rV-rV in FIG. 1, FIG. 5 is a sectional view along V-■ in FIG. 3, and FIG. 6 is a sectional view along VI-- in FIG. 1. 7 is a sectional view taken along the line ■-■ in FIG. 3, FIG. 8 is a sectional view taken along the line ■-■ in FIG. 1, and FIG. 9 is a side view partially showing a modified example of the device of the present invention It is. ■...Case body 2...Base 3...Input side case lid 5...Output side case lid 8...Output shaft 11...Sun gear 15...Input shaft
21.22... Internal gear 26... Inner eccentric cam 28... Outer eccentric cam 30... Worm wheel 32... Worm 36... Handle
37... Drive rotating body 39... Drive friction wheel
40... Internal gear 44... Intermediate transmission gear
48... Driven rotating body 52... Driven friction wheel
54... Spring 55... Planetary carrier 57...
・Planetary gear patent applicant Brideston Cycle Co., Ltd. Figure 4
Claims (1)
回転自在に設け、この駆動摩擦車と同心の内歯歯車をこ
の駆動摩擦車と一体的に形成し、前記入力軸と同心の２
個の内歯歯車をこの入力軸と一体的に形成し、この一方
の内歯歯車と前記駆動摩擦車と一体の内歯歯車を中間伝
動歯車を介して噛合連結し、前記入力軸を中心にして中
空円筒状の従動回転体を回転自在に設けると共に、この
従動回転体の内周に従動回転体と共に回転する従動摩擦
車を設け、この従動摩擦車と前記駆動摩擦車とを圧接係
合させ、前記従動回転体に遊星キャリヤを一体的に設け
、この遊星キャリヤに枢支した遊星歯車を前記入力軸と
一体の他方の内歯歯車に噛合させると共に、前記入力軸
と同心の出力軸と一体の太陽歯車に噛合させたことを特
徴とする無段変速装置。1. A driving friction wheel whose eccentricity can be freely adjusted with respect to the input shaft is rotatably provided, an internal gear concentric with the driving friction wheel is integrally formed with the driving friction wheel, and an internal gear concentric with the input shaft is formed integrally with the driving friction wheel. 2
one internal gear is integrally formed with the input shaft, one of the internal gears and the internal gear integral with the drive friction wheel are meshingly connected via an intermediate transmission gear, and the input shaft is the center of the internal gear. A hollow cylindrical driven rotary body is rotatably provided, and a driven friction wheel that rotates together with the driven rotary body is provided on the inner periphery of the driven rotary body, and the driven friction wheel and the driving friction wheel are press-fitted and engaged. , a planetary carrier is integrally provided on the driven rotating body, a planetary gear pivotally supported on the planetary carrier is meshed with the other internal gear that is integral with the input shaft, and is integral with an output shaft that is concentric with the input shaft. A continuously variable transmission characterized by meshing with a sun gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27292186A JPS63130956A (en) | 1986-11-18 | 1986-11-18 | Continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27292186A JPS63130956A (en) | 1986-11-18 | 1986-11-18 | Continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63130956A true JPS63130956A (en) | 1988-06-03 |
| JPH0137623B2 JPH0137623B2 (en) | 1989-08-08 |
Family
ID=17520611
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27292186A Granted JPS63130956A (en) | 1986-11-18 | 1986-11-18 | Continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63130956A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5163884A (en) * | 1990-05-08 | 1992-11-17 | Bridgestone Cycle Co., Ltd. | Friction-type stepless speed change device |
| US6231468B1 (en) * | 1997-03-18 | 2001-05-15 | Roger Bajulaz | Desmodromic mechanism |
| JP2007272453A (en) * | 2006-03-30 | 2007-10-18 | Nidec Sankyo Corp | Used medium discarding device and medium issuing device |
-
1986
- 1986-11-18 JP JP27292186A patent/JPS63130956A/en active Granted
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5163884A (en) * | 1990-05-08 | 1992-11-17 | Bridgestone Cycle Co., Ltd. | Friction-type stepless speed change device |
| US6231468B1 (en) * | 1997-03-18 | 2001-05-15 | Roger Bajulaz | Desmodromic mechanism |
| JP2007272453A (en) * | 2006-03-30 | 2007-10-18 | Nidec Sankyo Corp | Used medium discarding device and medium issuing device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0137623B2 (en) | 1989-08-08 |
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