200530522 (1) 九、發明說明 【發明所屬之技術領域】 本發明，是有關連續變化輸入軸的旋轉速度並 輸出軸的無段變速裝置，特別是關於可被搭載於汽 輪車等的無段變速裝置（CVT)。 【先前技術】 被搭載於比較小的排氣量的汽車等的習知的無 裝置’已知有藉由金屬皮帶連動一對帶輪的皮帶式 此CVT，是具備··與輸入軸連結的輸入帶輪、與輸 結的輸出帶輪、捲繞於兩帶輪間的無端狀的皮帶等 可變控制兩帶輪的V溝的寬來使皮帶接觸的旋轉 ，連續變化從輸入軸傳達至輸出軸的旋轉速度（例 本雜誌「日経〆力二力少」（1992年3月2曰，P34-昭）〇 J\ \\ / 且，被搭載於比較大的排氣量的汽車等的習知 變速裝置，已知有由具有球面狀的接觸面用的動力 動一對的碟片的環形式CVT。此CVT，是具備： 軸連結的輸入碟片、與輸出軸連結的輸出碟片、位 片之間的動力滾子等，藉由可變控制動力滾子的旋 傾斜來變化動力滾子接觸的兩碟片的旋轉徑，連續 輸入軸傳達至輸出軸的旋轉速度（例如，日本雜誌 〆力二力少」（1992年3月2日，P34〜P46， J Technical Journal No . 671(2001 年，P5 〜P13參照） 傳達至 車、二200530522 (1) IX. Description of the invention [Technical field to which the invention belongs] The present invention relates to a continuously variable transmission device that continuously changes the rotation speed of an input shaft and an output shaft, and particularly relates to a continuously variable transmission that can be mounted on a steam turbine or the like. Device (CVT). [Prior art] A conventional device-less device mounted on a relatively small-displacement automobile or the like is known. A belt type in which a pair of pulleys are linked by a metal belt is known. This CVT is equipped with an input shaft. The input pulley, the output pulley connected to the output, the endless belt wound between the two pulleys, etc., can control the width of the V groove of the two pulleys to change the rotation of the belt contact. Continuous changes are transmitted from the input shaft to Rotational speed of the output shaft (for example, "Sunburst Force Two Force" in this magazine (March 2, 1992, P34-Zhao) 〇J \ \\ / is mounted on a car with a relatively large displacement As a conventional transmission, a ring-shaped CVT having a pair of disks driven by a power for spherical contact surfaces is known. The CVT includes an input disk connected to a shaft and an output disk connected to an output shaft. The power rollers between the blades and bits, etc., can change the rotation diameter of the two discs that the power rollers contact by variably controlling the rotation inclination of the power rollers, and the continuous input shaft transmits the rotational speed of the output shaft (for example, Japan Magazines Force Two Less "(March 2, 1992, P34 ~ P46, J Techn ical Journal No. 671 (2001, referenced from P5 to P13)
段變速 CVT。 出軸連 ，藉由 徑變化 如，日 P46參 的無段 滾子連 與輸入 在兩碟 轉軸的 變化從 「曰経 ：NSK 200530522 (2) 但是，在上述習知的皮帶式CVT，雖是以變速範圍1 爲中心增速及減速，但是變速比變大（或是變小）的話，捲 ， 繞於一方側的帶輪的皮帶的曲率半徑會變大（或是曲率半 徑變小），而使發生於皮帶的金屬表面的滑動變多而使驅 動力的傳達效率下降。因此’爲了避免該範圍的方式驅動 的話，可設定的變速範圍就不寬（有限）。 且，因爲變速比並非無限制，所以爲了設定停止狀態 g 而需要離合器機構，且因爲輸入帶輪及輸出帶輪只朝同一 方向旋轉，所以爲了逆旋轉而需要反轉齒輪等，因而需要 供變化帶輪的溝寬用的油壓驅動機構等。進一步，因爲一 對的帶輪的徑比較大，且也具備油壓驅動機構等，所以裝 置整體會變大，又，當金屬皮帶的表面是接觸及脫離帶輪 時，會產生高頻的金屬音。 在上述習知的環形式CVT，是以變速範圍1爲中心增 速及減速，但在此中心附近對於動力滾子的碟片的空轉損 Φ 失變多而會使驅動力的傳達效率下降。且，因爲變速比並 非無限制，所以爲了設定停止狀態需要離合器機構，爲了 逆旋轉需要反轉齒輪等。進一步，爲了將動力滾子按壓於 碟片，需要可發生1.5〜2.2 GP a的超高壓的按壓負荷的機 構及構造。 【發明內容】 本發明，是鑑於上述習知的裝置的狀況，其目的是提 供一種無段變速裝置，可達成裝置的簡素化、小型化、低 -5- 200530522 (3) 成本化等，且可以使變速設定的範圍較寬，又，藉由提高 * 牽引係數，就可使大的負荷不會外加於磨擦增加的推力軸 > 承的軸承部，並可抑制在推力軸承軸承部的牽引油所導致 ，的牽引係數的提高，減少旋轉阻力並降低磨擦損失，可以 傳達大的驅動扭矩。 爲了達成上述目的’本發明的第1觀點的無段變速裝 置，是具有：可與輸入軸一體旋轉的載體；及可與輸出軸 I 一體旋轉的太陽齒輪；及在已嚙合於前述太陽齒輪的狀態 下對於前述載體可轉動自如地被支撐，且，可隨著前述輸 入軸的旋轉公轉於前述太陽齒輪的周圍的複數遊星齒輪； 及具有嚙合於前述的複數遊星齒輪的內齒的環齒輪；及含 有連續變化前述載體及前述環齒輪的相對旋轉速度的滾動 接觸的轉子的轉子式連續可變機構。 依據此結構的話，因爲藉由太陽齒輪、遊星齒輪、環 齒輪等形成差動齒輪列，藉由轉子式連續可變機構來連續 φ 變化與遊星齒輪的公轉一體旋轉的載體及環齒輪的相對的 旋轉速度，就可以連續產生因增減速所產生的正旋轉、停 止狀態、逆旋轉的方式，將輸入軸的旋轉傳達至輸出軸。 如此，不需要離合器機構、反轉切換機構等，輸入軸 ^ 及輸出軸因爲可以配置於同軸上，所以構造被簡略化，可 % 以提供便宜且小型的無段變速裝置。 在上述第1觀點的裝置中，前述轉子式連續可變機構 ，是含有：與前述載體一體旋轉的同時可朝前述輸入軸的 軸線方向往復移動自如，且，在其外周具有圓筒狀的接觸 -6- 200530522Segment variable speed CVT. The output shaft is connected by the diameter change. For example, the stepless roller connection and input of the Japanese P46 are changed on the two-disc rotation shaft from "Yi: NSK 200530522 (2). However, in the conventional belt-type CVT, although it is Speed up and down with the shift range 1 as the center, but if the gear ratio becomes larger (or smaller), the radius of curvature of the belt around the pulley on one side becomes larger (or the radius of curvature becomes smaller). As the sliding on the metal surface of the belt is increased, the transmission efficiency of the driving force is reduced. Therefore, if the driving method is to avoid this range, the settable speed range is not wide (limited). Also, because the speed ratio is not There is no limit, so a clutch mechanism is required to set the stop state g, and the input pulley and the output pulley only rotate in the same direction, so reverse gears are required for reverse rotation, so it is necessary to change the groove width of the pulley Hydraulic drive mechanism, etc. Furthermore, since the diameter of a pair of pulleys is relatively large, and the hydraulic drive mechanism is also provided, the entire device becomes larger. A high-frequency metallic sound is generated when the pulley is contacted and disengaged. In the conventional ring-shaped CVT, the speed is increased and decreased with the shift range 1 as the center, but the idling of the power roller ’s disc near this center. The loss of Φ increases and the transmission efficiency of driving force decreases. In addition, because the gear ratio is not unlimited, a clutch mechanism is required to set the stop state, a reverse gear is required for reverse rotation, and the like. Further, to press the power roller For the disc, a mechanism and a structure capable of generating an ultra-high pressure load of 1.5 to 2.2 GP a are required. [Summary of the Invention] The present invention is to provide a stepless speed change device in view of the state of the conventional device described above. The device can be simplified, miniaturized, and low-2005200522 (3) cost reduction, etc., and the range of gear shift setting can be widened. By increasing the * traction coefficient, large loads can be prevented from being applied. Increased frictional thrust shaft bearing parts, and can suppress the increase of the traction coefficient caused by the traction oil in the thrust bearing bearing part, reduce the rotation resistance and reduce the friction In order to achieve the above-mentioned object, the stepless speed change device according to the first aspect of the present invention includes: a carrier capable of rotating integrally with the input shaft; and a sun gear capable of rotating integrally with the output shaft I; And a plurality of planetary gears which are rotatably supported by the carrier while being engaged with the sun gear, and which can revolve around the sun gear as the input shaft rotates; and Ring gear with internal teeth of a planetary gear; and a rotor-type continuously variable mechanism including a rolling contact rotor that continuously changes the relative rotational speed of the carrier and the ring gear. According to this structure, since the sun gear, the planetary gear, The ring gear and the like form a differential gear train, and the rotor-type continuously variable mechanism continuously changes φ to change the relative rotation speed of the carrier and the ring gear that rotate integrally with the revolution of the planetary gear. Rotate, stop, and counter-rotate to convey the rotation of the input shaft to the output shaft. In this way, a clutch mechanism, a reverse switching mechanism, and the like are not needed, and the input shaft ^ and the output shaft can be arranged on the same axis, so the structure is simplified, and an inexpensive and compact stepless transmission can be provided. In the device according to the first aspect, the rotor-type continuously variable mechanism includes a mechanism capable of reciprocating toward the axis of the input shaft while rotating integrally with the carrier, and having a cylindrical contact on an outer periphery thereof. -6- 200530522
面的可動碟片；及形成於前述環齒輪的外周的圓錐狀的接 ‘觸面；及可轉動自如地被支撐在對於前述輸入軸或是輸出 ^ 軸的軸線傾斜的軸線周圍，且’具有與前述環齒輪的接觸 面接觸的第1圓錐面及與前述可動碟片的接觸面接觸的第2 圓錐面的二段圓錐狀的牽引轉子；及與前述環齒輪及可動 碟片協動並從外側挾入地與前述牽引轉子接觸的牽引環。 依據此結構的話，可動碟片的接觸面會接觸於牽引轉 g 子的第2圓錐面，環齒輪的接觸面會接觸於牽引轉子的第丄 圓錐面，進一步，將牽引轉子按壓於可動碟片及環齒輪的 方式使牽引環接觸牽引轉子（例如第1圓錐面）。而且，因 爲可動碟片是朝輸入軸的軸線方向移動，相接觸的第2圓 錐面上的旋轉半徑會變化，載體的旋轉速度（遊星齒輪的 公轉速度）及環齒輪的旋轉速度會相對地變化。例如，藉 由將可動碟片移動至預定的位置，對於可動碟片（載體）的 旋轉不會遲延環齒輪地一起旋轉，就可設定成正旋轉（例 φ 如，變速比1)，藉由使環齒輪的旋轉先走預定量，就可設 定成停止狀態（即，變速比〇)，藉由使環齒輪的旋轉更先 走預定量，就可設定成逆旋轉（例如，變速比-0.2)，變速 比的設定範圍可以比較寬。 在上述第1觀點的裝置中，前述牽引環，是在前述輸 入軸或是輸出軸的軸線方向，被配置於前述環齒輪的接觸 面及可動碟片的接觸面之間。 依據此結構的話，牽引環的按壓力，因爲可將牽引轉 子平衡性佳地按壓作用於環齒輪及可動碟片’所以可確實 -7- 200530522 (5) 獲得牽引力，進行更穩定的變速動作。 在上述第1觀點的裝置中’含有：將前述可動碟片朝 向前述輸入軸的軸線方向的一方側推迫的推迫構件、及抵 抗前述推迫構件的推迫力並移動按壓前述可動碟片的按壓 構件。 依據此結構的話’藉由適宜調整按壓構件的位置’就 可以變化可動碟片的位置。因此，容易將與按壓構件連動 I 的驅動機構等設定於裝置的內部及外部。 在上述第1觀點的裝置中，前述牽引轉子的第1圓錐面 ，是在其旋轉中心線與前述輸入軸或是輸出軸的軸線交叉 的點上具有頂點。 依據此結構的話，可防止在牽引轉子及環齒輪及牽引 環的接觸領域的空轉損失，可提高牽引驅動的效率（滾動 接觸所產生的牽引力的傳達效率）。 在上述第1觀點的裝置中，前述牽引環，是在其中心 Φ 爲從前述輸入軸或是輸出軸的軸線偏離了預定量的狀態下 ’朝其徑方向可移動自如且轉動不能地被支撐於前述輸入 軸或是輸出軸的軸緣周圍，前述牽引轉子，是由在前述牽 引環及前述可動碟片及環齒輪之間公轉可能的方式配列於 周方向的複數牽引轉子所構成，前述的複數牽引轉子的至 少一個’是對於其他牽引轉子可獨立公轉地被支撐。 依據此結構的話，輸入軸旋轉的話，在可動碟片（的 接觸面）及牽引轉子（的第2圓錐面）之間會產生磨擦。如此 的話’可獨立公轉的牽引轉子會被拖拉到可動碟片，且被 200530522 (6) 嵌入至牽引環及可動碟片之間的話，藉由該楔作用，使牽 引環朝適宜徑方向移動，並使其他的牽引轉子被旋緊（強 力挾持）於可動碟片及牽引環之間。由此，在牽引轉子及 環齒輪之間也可發生大的牽引力，可確實地進行牽引驅動 〇 進一步’負荷是外加於輸出軸的情況時，輸出軸的旋 轉會變慢而使環齒輪的旋轉變慢的話，可獨立公轉的牽引 g 轉子會朝狹窄間隙的方向移動，而會增加其他的牽引轉子 的旋緊力。由此，傳達扭矩增加就可消解遲延，並可進行 所期的扭矩傳達。 在上述結構中，前述牽引轉子，是由在前述牽引環及 前述可動碟片及環齒輪之間配列於周方向的三個牽引轉子 所構成，前述牽引轉子中的二個，是可轉動自如地被支撐 於第1連桿，該第丨連桿是可轉動自如地被設在前述輸出軸 周圍，前述牽引轉子的剩下的一個，是可轉動自如被支撐 φ 在第2連桿，該第2連桿是可轉動自如地設在前述輸出軸周 圍。 依據此結構的話，可削減零件點數，且可以確保穩定 的牽引驅動。 且，在上述第1觀點的裝置中，前述牽引環，在其中 心是位置於與前述輸入軸或是輸出軸的軸線同軸上的狀態 下，可轉動自如地被支撐於前述輸入軸或是輸出軸的軸緣 周圍，前述牽引轉子，是含有：在前述牽引環及前述可動 碟片及環齒輪之間公轉不能地朝周方向配列的固定轉子、 -9- 200530522 (7) 及對於前述固定轉子相對移動可能地被支撐的可動轉子。 依據此結構的話，輸入軸旋轉的話，在可動碟片（的 接觸面）及牽引轉子（的第2圓錐面）之間會產生磨擦。如此 的話，牽引環會旋轉並將可動轉子朝可動碟片拖拉，且被 嵌入牽引環及可動碟片之間的話，藉由該楔作用，使固定 轉子也被旋緊（強力挾持）於可動碟片及牽引環之間。由此 ，大的牽引力會發生，就可確實進行牽引驅動。 | 在上述結構中，前述牽引轉子，是含有：二個前述固 定轉子、及一個可轉動自如地支撐於連桿的前述可動轉子 ，且前述連桿，是在前述輸出軸周圍的預定角度範圍內可 移動自如。 依據此結構的話，可減少零件點數，且可以確保穩定 的牽引驅動。即，負荷外加於輸出軸的話，環齒輪對於牽 引轉子的旋轉雖會產生遲延，但是一個可動轉子會朝周方 向移動該遲延部分，並增加二個固定轉子的旋緊力。由此 φ ，傳達扭矩增加就可消解遲延，並進行所期的扭矩傳達。 爲了達成上述目的本發明的第2觀點的無段變速裝置 ，是具有：與輸入軸一體旋轉的載體、及與輸出軸一體旋 轉的太陽齒輪、及可轉動自如地設置於前述輸出軸的周圍 的旋轉體、及在嚙合於前述太陽齒輪的狀態下對於前述旋 轉體可轉動自如地被支撐且隨著前述旋轉體的旋轉可在前 述太陽齒輪的周圍公轉的複數遊星齒輪、及與前述輸入軸 一體旋轉地與前述載體連結且具有嚙合於前述的複數遊星 齒輪的內齒的環齒輪、及含有連續變化前述載體及前述旋 •10- 200530522 (8) 轉體的相對旋轉速度地滾動接觸的轉子的轉子式連續可變 機構。 依據此結構的話，因爲藉由太陽齒輪、遊星齒輪、環 齒輪等形成差動齒輪列，所以藉由轉子式連續可變機構， 連續變化與環齒輪一體旋轉的載體及與遊星齒輪的公轉一 體旋轉的旋轉體的相對旋轉速度，就可由連續產生因增減 速所產生的正旋轉、停止狀態、逆旋轉的方式，將輸入軸 g 的旋轉傳達至輸出軸。如此，因爲不需要離合器機構、反 轉切換機構等，可將輸入軸及輸出軸配置於同軸上，所以 可以提供構造簡略、便宜且小型的無段變速裝置。 在上述第2觀點的裝置，前述轉子式連續可變機構， 是含有：與前述載體一體旋轉的同時朝前述輸入軸的軸線 方向往復移動自如且在外周具有圓筒狀的接觸面的可動體 、及形成於前述旋轉體的外周的圓錐狀的接觸面、及可轉 動自如地被支撐在對於前述輸入軸或是輸出軸的軸線傾斜 φ 的軸線周圍’且，具有可與前述旋轉體的接觸面接觸的第 1圓錐面及可與前述可動體的接觸面接觸的第2圓錐面的二 段圓錐狀的牽引轉子、及與前述旋轉體及可動體協動並從 外側挾入地接觸前述牽引轉子的牽引環。 依據此結構的話，可動體的接觸面會接觸於牽引轉子 的第2圓錐面，旋轉體的接觸面會接觸於牽引轉子的第1圓 錐面’進一步，使牽引轉子按壓可動體及旋轉體的方式使 牽引環接觸於牽引轉子（例如第1圓錐面）。而且，藉由使 可動體朝輸入軸的軸線方向移動，就可使相接觸的第2圓 -11 - 200530522 (9) 錐面上的旋轉半徑變化，而使載體的旋轉速度（環齒輪的 -旋轉速度）及旋轉體的旋轉速度（遊星齒輪的公轉速度）相 ，對地變化。即，適宜地移動可動體，藉由對於可動體（環 齒輪）的旋轉速度適宜地變化旋轉體的旋轉速度，就可變 化較寬範圍的變速比，並連續地設定正旋轉、停止、逆旋 轉。 在上述第2觀點的裝置的轉子式連續可變機構，前述 φ 牽引環，是在前述輸入軸或是輸出軸的軸線方向，被配置 於前述旋轉體的接觸面及可動體的接觸面之間。 依據此結構的話，牽引環的按壓力，因爲可將牽引轉 子平衡性佳地按壓作用於旋轉體及可動體，所以可確實獲 得牽引力，進行更穩定的變速動作。 在上述第2觀點的裝置中，前述轉子式連續可變機構 ’是含有：與前述旋轉體一體旋轉的同時朝前述輸出軸的 軸線方向往復移動自如且在其外周具有圓筒狀的接觸面的 φ 可動體、及形成於前述載體的圓錐狀的接觸面、及可轉動 自如被支撐在對於前述輸入軸或是輸出軸的軸線傾斜的軸 線周圍且具有與前述載體的接觸面接觸的第1圓錐面及與 前述可動體的接觸面接觸的第2圓錐面的二段圓錐狀的牽 引轉子、及與前述載體及可動體協動並從外側挾入地接觸 ' 前述牽引轉子的牽引環。 依據此結構的話，可動體的接觸面會接觸於牽引轉子 的第2圓錐面，載體的接觸面會接觸於牽引轉子的第1圓錐 面’進一步，將牽引轉子按壓於可動體及旋轉體的方式使 -12- 200530522 (10) 牽引環接觸於牽引轉子（的例如軸承）。而且，藉由使可動 體朝輸出軸的軸線方向移動，就可使相接觸的第2圓錐面 上的旋轉半徑變化，使載體的旋轉速度（環齒輪的旋轉速 度）及旋轉體的旋轉速度（遊星齒輪的公轉速度）相對地變 化。即，藉由適宜地移動可動體，對於載體（環齒輪）的旋 轉速度適宜變化旋轉體的旋轉速度，就可較寬範圍地變化 變速比，並可以連續地設定正旋轉、停止、逆旋轉。特別 | 是，因爲可以縮小牽引轉子的變速比，所以可以減少牽引 傳達領域的空轉損失，且，有利於牽引係數、傳達效率。 且，依據此結構的話，藉由使被設在載體的圓錐狀的 接觸面形成於輸出軸的附近，就可配置牽引轉子接近輸出 軸的軸線附近，而可以達成由零件的集約化所導致的裝置 的小型化。 在上述第2觀點的裝置的轉子式連續可變機構中，前 述牽引環，是在前述輸入軸或是輸出軸的軸線方向，被配 φ 置於前述載體的接觸面及可動體的接觸面之間。 依據此結構的話，牽引環的按壓力，因爲是將牽引轉 子平衡性佳地按壓作用於載體及可動體，所以可確實獲得 牽引力，進行更穩定的變速動作。 在上述第2觀點的裝置中，包含··將前述可動體朝向 前述輸入軸的軸線方向的一方側推迫的推迫構件、及抵抗 前述推迫構件的推迫力並移動按壓前述可動體的按壓構件 〇 依據此結構的話’藉由適宜調整按壓構件的位置，就 -13- 200530522 (11) 可以變化可動碟片的位置。因此，容易將與按壓構件連動 的驅動機構等設定於裝置的內部及外部。 在上述第2觀點的裝置中，前述牽引轉子的第1圓錐面 ，是在其旋轉中心線與前述輸入軸或是輸出軸的軸線交叉 的點上具有頂點。 依據此結構的話，可防止在牽引轉子及環齒輪及牽引 環的接觸領域的空轉損失，可提高牽引驅動的效率（滾動 接觸所產生的牽引力的傳達效率）。 在上述第2觀點的裝置中，前述牽引環，在其中心是 位置在與前述輸入軸或是輸出軸的軸線同軸上的狀態下， 可轉動自如被支撐於前述輸入軸或是輸出軸的軸緣周圍， 前述牽引轉子，是含有：在前述牽引環及前述可動體及旋 轉體之間公轉不能地朝周方向配列的固定轉子、及對於前 述固定轉子相對移動可能地被支撐的可動轉子。 依據此結構的話，輸入軸旋轉的話，在可動碟片（的 接觸面）及牽引轉子（的第2圓錐面）之間會產生磨擦。如此 的話，牽引環旋轉且使可動轉子被拖拉到可動體，且嵌入 牽引環及可動體之間的話，藉由該楔作用，使固定轉子也 被旋緊（強力挾持）於可動體及牽引環之間。由此，大的牽 引力會發生，可確實地進行牽引驅動。 進一步，負荷外加於輸出軸的情況時，因輸出軸的旋 轉變慢而使環齒輪的旋轉變慢的話，可動轉子會朝狹窄間 隙的方向移動，而會增加其他的固定轉子的旋緊力。由此 ，傳達扭矩增加就可消解遲延，並可進行所期的扭矩傳達 -14 - 200530522 (12) •在上述第2觀點的裝置中，前述牽引轉子，是含有： ，二個前述固定轉子、及可轉動自如地被支撐於連桿的一個 前述可動轉子，而前述連桿，是在前述輸出軸周圍的預定 角度範圍內可移動自如。 依據此結構的話，可減少零件點數，且可以確保穩定 的牽引驅動。即，負荷外加於輸出軸的話，環齒輪雖會對 g 於牽引轉子的旋轉產生遲延，但是一個可動轉子只朝周方 向移動該遲延部分，並增加二個固定轉子的旋緊力。由此 ，傳達扭矩增加就可消解遲延，進行所期的扭矩傳達。 在上述第2觀點的裝置中，前述牽引環，其中心可朝 徑方向移動自如且在前述輸入軸或是輸出軸的軸線周圍轉 動不能地被支撐，且，具有凸輪面，其可內接前述牽引轉 子的同時增加法線負荷地影響凸輪作用；前述牽引轉子， 在預定的角度範圍公轉可能地被支撐的同時，具有接觸軸 φ 承可對於前述第1圓錐面及第2圓錐面相對旋轉並與前述凸 輪面接觸。 依據此結構的話，因輸出軸的負荷扭矩增加，而比由 轉子式連續可變機構所設定的預定速度慢的話，直到此旋 轉遲延消解爲止，使牽引轉子的軸承自轉並沿著牽引環的 凸輪面在預定的角度範圍內公轉，使凸輪面對於牽引承接 器（軸承）進行凸輪作用，自動地增加需要最小限度的法線 負荷。如此，依據輸出軸的負荷變動，使需要的法線負荷 被反饋控制，並獲得穩定的牽引力，並可確實進行旋轉力 -15- 200530522 (13) 的傳達。 如上述，依據上述的無段變速裝置’就可獲得一種無 段變速裝置，不需如習知設置離合器機構、反轉齒輪、油 壓機構等，連續產生因增減速所產生的正旋轉、停止、逆 旋轉的方式，將輸入軸的旋轉傳達至輸出軸’且可設定較 寬的變速範圍，可極力防止騷音等，可以傳達大的驅動扭 矩，小型且便宜。 【實施方式】 以下，對於本發明的最良的實施例，參照添付圖面說 明之。 第1圖至第6圖，是顯示本發明的第1觀點的無段變速 裝置的一實施例，第1圖是裝置的剖面圖，第2圖至第6圖 是裝置的模式圖。 此無段變速裝置，是如第1圖所示，具備：外殼1 0、 φ 對於外殼1 〇的可轉動自如地被支撐的輸入軸2 0、對於輸入 軸20—體旋轉地結合的載體30、對於外殻10可轉動自如地 被支撐的輸出軸40、對於輸出軸40—體旋轉地結合的太陽 齒輪50、在嚙合於太陽齒輪50的狀態下對於載體3〇可轉動 • 自如地被支撐的3個遊星齒輪60、嚙合於遊星齒輪60的環 ’齒輪7 0、與載體3 0 —體旋轉且朝輸入軸2 0的軸線方向移動 可能地被支撐的可動碟片8 0、配列於環齒輪7 0及可動碟片 8 0的外周的3個牽引轉子9 0、配置於牽引轉子9 〇的外側的 牽引環100等。 -16- 200530522 (14) 而且，藉由可動碟片80、環齒輪70的後述接觸面72、 牽引轉子90、牽引環1〇〇等，構成可連續變化載體30及環 齒輪7 0的相對旋轉速度的轉子式連續可變機構。 外殻1 〇，是使用鋁材料等的鑄模成型而形成’如第1 圖所示，由：安裝有供支撐輸入軸20用的軸承Ua及密封 件lib等的外殻半體11、安裝有供支撐輸出軸40用的軸承 12a及密封件12b等的外殼半體12等構成。 而且，外殼1 〇，是藉由螺絲等將外殼半體1 1及外殻半 體12結合而形成，並使輸入軸20及輸出軸40可轉動自如地 被支撐於同一軸線上。 輸入軸20，是如第1圖所示，在其端部具有板狀的凸 緣2 1，對於此凸緣2 1 ’結合有以略1 20度的間隔配置且與 軸線L平行伸長的圓柱狀的3根銷2 2。即，藉由凸緣2 1及3 根銷22構成載體30。 各載體3 0 (銷2 2 )，是在其先端部，可轉動自如地支撐 遊星齒輪60的同時，保持嚙合於太陽齒輪50的狀態。即’ 輸入軸20旋轉的話，載體30會一體旋轉，使遊星齒輪60在 太陽齒輪50的周圍公轉（遊星運動）° 環齒輪70，是如第1圖及第4圖B所示，具有嚙合於3 個遊星齒輪60的內齒71，在其外周中’具有與後述牽引轉 子9 0的第1圓錐面9 1接觸的圓錐狀的接觸面7 2。 可動碟片8 0，是如第1圖所示’具有可滑動自如地外 嵌於載體3 0 (銷2 2 )的3個圓孔8 1，在其外周中’具有與後 述牽引轉子90的第2圓錐面92接觸的圓筒狀的接觸面82 ° -17- 200530522 (15) 而且，可動碟片80，是可沿著銷22朝軸線L方向往復動自 •如地被支撐。 .且，可動碟片8 0，是如第1圖所示，藉由作爲推迫構 件的捲簧83朝向輸入軸20側推迫，一方面，在相面對於捲 簧83的推迫力側配置有按壓構件84。按壓構件84，是藉由 與蝸桿85及蝸輪86、形成於蝸輪86的內周的送出母螺栓嚙 合的同時規制旋轉的螺栓構件87，抵抗捲簧83的推迫力且 g 朝軸線L方向移動。在此，在蝸桿8 5的上流側中，連結有 操作用的驅動馬達，依據操作者的操作訊號被驅動控制。 且，按壓構件84的驅動機構，是採用藉由設在外殼10 的外側的排擋操作桿等被驅動的結構也可以。 3個牽引轉子90，是如第1圖至第3圖、第5圖所示，使 各旋轉中心線S在與輸出軸40的軸線L上交叉於同一點P 地傾斜的狀態下可旋轉（自轉）及公轉地被支撐。即，2個 牽引轉子90，是可轉動自如地被支撐於第1連桿93，第1連 φ 桿93是對於可轉動自如地被設在輸出軸40周圍，1個牽引 轉子90，是可轉動自地被支撐於第2連桿94，第2連桿94是 對於第1連桿93獨立且可轉動自如地設在輸出軸40周圍， 該2個牽引轉子90是可別個獨立公轉。對於牽引轉子90的 旋轉中心線S的軸線L的傾斜角度，可依據所設定的變速 比的範圍適宜選用。且，在第1連桿93及第2連桿94之間， 設有彈簧95可使其相互靠近。 在此，3個牽引轉子90，是如第5圖所示，形成外徑相 互不同的大徑、中徑、小徑，例如，被支撐於第1連桿9 3 -18- 200530522 (16) 的2個牽引轉子90是形成大徑及中徑，被支撐於第2連桿94 的1個牽引轉子90是形成小徑也可以。且，只有1個牽引轉 子9 0形成比其他小徑也可以。 且，3個牽引轉子90，是如第1圖至第3圖所示，具有 :與環齒輪70的接觸面72及後述的牽引環1〇〇的接觸面ι〇1 接觸的第1圓錐面9 1、及與可動碟片8 0的接觸面8 2接觸的 第2圓錐面92。 g 第1圓錐面91，是在牽引轉子90的旋轉中心線S與輸 出軸4 0的軸線L交叉的點P上具有頂點。第2圓錐面9 2， 是使在可動碟片8 0的接觸面8 2接觸的位置的母線μ，與輸 入軸2 0的軸線L平行。且，第2圓錐面9 2的特徵，即，對 於旋轉中心線S的母線Μ的傾斜角度，是依據變速比的 設定，藉由保持母線Μ與軸線L平行並選定旋轉中心線 S的傾斜角度來決定。 因此，藉由採用上述的第1圓錐面91，在牽引轉子90 φ 及環齒輪70及牽引環100之間的接觸領域中，可防止空轉 損失，並提高由滾動接觸所產生的牽引力的傳達效率，即 ，牽引驅動的效率。且，藉由採用第2圓錐面92，在牽引 轉子90及可動碟片80之間，容許朝可動碟片80的軸線方向 L的移動且可相互滾動接觸。 牽引環1〇〇，是如第1圖至第3圖、第5圖所示，具有可 與牽引轉子90的第1圓錐面91接觸的圓錐狀的接觸面101， 其旋轉中心線Lf，是位置於從輸出軸40的軸線L偏離預 定量的位置。而且，被插入於外殼半體1 2的環狀溝1 2 C並 -19- 200530522 (17) 朝朝徑方向自由移動預定量地被支撐的同時，藉由銷1 2 d 被規制成不可旋轉。 且，牽引環100，是如第1圖至第3圖所示，在輸入軸 20及輸出軸40的軸線L方向，配置成位置於可動環80及環 齒輪7 〇之間。因此，牽引環1 0 0的按壓力，因爲是將牽引 轉子90的第1圓錐面91及第2圓錐面92，分別平衡性佳地按 壓作用在環齒輪70的接觸面72及可動碟片80的接觸面82， 所以可確實獲得牽引力，進行更穩定的變速動作。 在此，說明3個牽引轉子90、可動碟片80(及環齒輪 70)的相互關係。 首先，對於輸出軸40施加一定的負荷的情況時’輸入 軸2 0及可動碟片80旋轉的話，牽引轉子90會旋轉（自轉及 公轉），而旋轉環齒輪70，預定的扭矩被傳達而使輸出軸 4 0旋轉。 一方面，如第5圖所示，在輸入軸20及可動碟片80朝 C 3方向旋轉的狀態下，輸出軸4 0的負荷增加的話，輸出軸 40的旋轉會變慢，環齒輪70會對於牽引轉子90的旋轉產生 遲延（C3’方向）。此遲延，是因爲由牽引轉子90的法線負 荷所產生的牽引扭矩不足。且，可獨立公轉的最小的牽引 轉子90，是一邊朝C2方向旋轉（自轉）一邊朝狹窄間隙的 方向（C1方向）移動，而插入牽引環100及可動碟片80及環 齒輪70之間並產生楔作用。 藉由此楔作用，牽引環100會適宜朝徑方向（變心運動 )移動，且中徑及大徑的2個牽引轉子9 0，是更被強力旋緊 -20- 200530522 (18) (強力挾持）於可動碟片8 0及環齒輪7 0及牽引環1 0 0之間， ^ 牽引轉子90的法線負荷會增加且牽引係數會變大，使牽引 - 扭矩增加。由此，傳達扭矩增加，環齒輪70的遲延也被消 解’ 3個牽引轉子90會一起旋轉並確實地進行扭矩傳達， 且可確實地進行牽引驅動。 且，牽引轉子90，因爲是配置於環齒輪70的外周且只 在從輸入軸20及輸出軸40隔有預定距離的位置進行扭矩的 0 傳達，所以即使小型也可以傳達大的扭矩。 接著，對於上述無段變速裝置的動作及原理，參照第 6圖A至第6圖C說明之。且，在此，對於輸入軸20的預 定方向的旋轉，是假設輸出軸40朝車輛等的前進方向旋轉 的情況爲正旋轉，朝後退方向旋轉的情況爲逆旋轉。 首先，輸入軸20是以預定的速度旋轉的話，可動碟片 8 0及載體30皆會成爲一體並朝同一方向旋轉。而且，隨著 載體30的旋轉，3個遊星齒輪60也旋轉（自轉）且與輸入軸 φ 20朝同一方向以同一速度公轉。 在此，從遊星齒輪60朝太陽齒輪50的旋轉扭矩的傳達 ，是依據環齒輪7 0當時的狀態變化。即’環齒輪7 0 ’是依 據在：停止、與可動碟片8 0 (及輸入軸2 0 )以同一速度旋轉 、對於可動碟片80先行旋轉（以更快的速度旋轉）、對於可 _ 動碟片80遲延旋轉（以更慢的速度旋轉）等的任一的狀態下 ，變化從遊星齒輪6 0傳達至太陽齒輪5 0及輸出軸4 0的旋轉 速度。 在此，藉由適宜變化與牽引轉子90的第2圓錐面92接 -21 - 200530522 (19) 觸的可動碟片80的軸線方向L的位置，就可在載體30(及 '可動碟片80)及環齒輪70之間產生相對旋轉速度的變化（旋 ，轉差），並可連續變化從輸入軸20傳達至輸出軸40的旋轉 速度（隨著增減速連續產生的正旋轉、停止、逆旋轉等）。 即，環齒輪70及載體30的旋轉差，是依據可動碟片80 接觸於第2圓錐面92的位置而變化。因此，第1圓錐面91的 母線N及可動碟片80的法線V的交點上的牽引轉子90的 g 旋轉半徑爲R，在可動碟片80的接觸面82接觸的位置的第 2圓錐面92的旋轉半徑爲r的話，旋轉差可表示成（r-R)/R ，此値成爲負値的話，環齒輪70會對於載體30(及可動碟 片80)先行旋轉（快速旋轉）。 例如，如第6圖 A所示的狀態中，r>R，輸入軸20的 旋轉是由正旋轉被傳達至輸出軸40，可動碟片80的變速比 是隨著朝向r値變小的左側移動漸漸變小，如第6圖B所 示，當可動碟片80移動至r’<R’的預定的位置，且環齒輪 φ 70對於載體30(可動碟片80)先行旋轉預定量時，變速比就 成爲〇並停止輸出軸4 0的旋轉。 而且，進一步，如第6圖C所示’可動碟片80移動至 r値進一步縮小成爲rf’（<rf<r)的位置的話，環齒輪70會對 於載體30(可動碟片80)更先行旋轉預定量’使變速比成爲 負値並使輸出軸40逆旋轉。 在此，可動碟片80，是藉由抵抗捲簧83的推迫力並利 用驅動機構（蝸桿8 5、蝸輪8 6、螺栓構件8 7等）適宜地移動 的按壓構件8 4，進行上述的變速動作。 -22- 200530522 (20) 在此，例如太陽齒輪5〇的齒數爲18、遊星齒輪60的齒 -數爲2 7、環齒輪7 0的齒數爲7 2的話’對於載體3 0 (及可動 ，碟片8 0)的旋轉的環齒輪7 0的旋轉，是遲延1 / 5旋轉使變速 比成爲2，無旋轉遲延（同時旋轉）時變速比成爲1 ’先行1 /5 旋轉時變速比成爲0 (停止），遲延2 / 5旋轉時變速比成爲-1 ( 逆旋轉）。 因爲一般汽車的變速比，在停止狀態時變速比爲0(減 0 速比：無限大），超過（overtop)時變速比爲1.2(減速比： 0 · 8 3 3 3 )，後退時變速比爲-〇 . 2 (減速比：-5 )程度，此情況 ，環齒輪70的旋轉對於載體30的旋轉，是在遲延1/2 5旋轉 時設定爲超過（overtop) ’先行1/5旋轉時設定爲停止狀氣 ，先行2 / 5旋轉是設定爲後退。 依據上述結構的無段變速裝置’藉由採用利用牽引驅 動方式的連續可變機構，就不需要習知的C VT所需要的 及離合器機構、反轉切換齒輪等’又因爲可以同軸配置輸 φ 入軸2 0及輸出軸4 0，所以可以獲得：小型且便宜、空轉損 失少、極力防止騷音的發生、可較寬設定變速範圍、高效 率的扭矩傳達特性。 第7圖，是顯示本發明的第1觀點的無段變速裝置的其 他的實施例，對於前述的實施例，變更：牽引轉子90 ’的 • 傾斜方向、可動碟片80,及環齒輪7〇’以及牽引環100'，對 於其他的同一的結構是附加同一符號並省略其說明。 即，此實施例的裝置，是如第7圖所示’ 2個牽引轉子 9〇,是可轉動自如地被支撐於第1連桿93 ’ 1個牽引轉子90’ -23- 200530522 (21) 是可轉動自如被支撐於第2連桿94。 -而且，牽引轉子9 (Γ的旋轉中心線V，是與輸入軸2 0 _ 的軸線L交叉地傾斜配置，第1圓錐面9 Γ是與環齒輪7 0 ’ 的圓錐狀的接觸面72’及牽引環100’的圓錐狀的接觸面101， 接觸，第2圓錐面92’是與可動碟片80’的圓筒狀的接觸面 82’接觸。且，第1圓錐面91’，是在旋轉中心線S’與輸入 軸2 0的軸線L交叉的點上具有頂點。 0 即使此裝置，也可與前述同樣進行連續變速動作，可 以抑制空轉損失，並極力防止騷音的發生，可較寬設定變 速範圍，可以獲得高效率的扭矩傳達特性，特別是，藉由 變更牽引轉子90’的傾斜的方向，就可更集約化各零件， 可以使裝置更小型化。 牽引轉子90’’，是在具有接觸面101"的牽引環100"及 可動碟片80(接觸面82)及環齒輪70(接觸面72)之間，如第8 圖至第10圖所示，藉由：2個固定轉子90’’（90a’’、90b’’）、 φ 及1個可動轉子90"(90c")形成，固定轉子90"(90a"、 9 Ob")是呈周方向配列的同時可轉動自如地被支撐於外殻 半體12，可動轉子90" (90c")是可轉動自如地被支撐於連 桿94’，而連桿94’是以預定的角度範圍可動地設置在對於2 • 個固定轉子90"相對移動可能地配置於輸出軸40的周圍的 - 筒狀構件12e。且，連桿94’，是藉由彈簧95朝預定的方向 旋轉推迫。 由此，3個牽引轉子90’’是成爲公轉不能，且1個可動 轉子90’’（9〇c")是成爲抵抗彈簧95的推迫力並對於2個固定 -24- 200530522 (22) 轉子90"(90a’’、90b")相對移動。 依據此裝置，對於輸出軸40加上一定的負荷的情況時 ，輸入軸2 0及可動碟片8 0旋轉的話，3個牽引轉子9 0’’會旋 轉（自轉），並旋轉環齒輪70，使預定的扭矩被傳達並使輸 出軸4 0旋轉。 一方面，如第10圖所示，在輸入軸20及可動碟片80朝 C 3方向旋轉的狀態下，輸出軸4 0的負荷增加的話，輸出軸 g 4 0的旋轉會變慢，環齒輪7 0會對於牽引轉子9 〇 "的旋轉（自 轉）產生遲延（C3’方向）。此遲延，是因爲由牽引轉子90"的 法線負荷所產生的牽引扭矩不足。且，在環齒輪70及固定 轉子9 0 " (9 0 a "、9 0 b ’ ’）之間產生微小的滑動，可動轉子 9 0 f ’（ 9 0 c ’ ’）是一邊朝C 2方向的（自轉）旋轉一邊朝狹窄間隙 的方向（C1方向）移動，插入牽引環1〇〇"及可動碟片8〇及環 齒輪70之間並產生楔作用。 藉由此楔作用，2個固定轉子90"(90 a，，、90b，，），是被 φ 強力旋緊（強力挾持）於可動碟片80及環齒輪70及牽引環 100"之間，牽引轉子90’’的法線負荷會增加且牽引係數會 變大’使牽引扭矩增加。由此，傳達扭矩增加，環齒輪7〇 的遲延也被消解，可動轉子90"(90c")的移動（嵌入）也會 停止’可確實進行扭矩傳達’並可確實地進行牽引驅動。 且，牽引轉子90’’，因爲是配置於環齒輪7〇的外周且 在從輸入軸20及輸出軸40隔有預定的距離的位置進行扭矩 的傳達，所以雖小型也可以傳達大的扭矩。 且’在此裝置中，牽引環1 〇〇，，因爲只進行旋轉不進行 -25- 200530522 (23) 變心運動，所以可縮小該部分的外殼1 0的外徑尺寸。 -第1 1圖，是對於前述的第8圖及第9圖的實施例’變更 了：牽引轉子9 0，"的傾斜方向、可動碟片8 (V及環齒輪7 0’ 以及牽引環1 〇 〇，"，對於其他的同一的結構是附加同一符 號並省略其說明。 即，在此實施例的裝置中，是如第1 1圖所示’牽引轉 子（固定轉子及可動轉子）9〇"’的旋轉中心線S’，是與輸入 g 軸20的軸線L交叉地傾斜配置，第1圓錐面91’是與環齒輪 70’的圓錐狀的接觸面72’及牽引環100’’’的圓錐狀的接觸面 101’"接觸，第2圓錐面92’是與可動碟片80’的圓筒狀的接 觸面82’接觸。且，第1圓錐面91’，是在旋轉中心線S’與 輸入軸20的軸線L交叉的點上具有頂點。 對於此裝置，也與前述同樣進行連續的變速動作，可 以獲得：抑制空轉損失、極力防止騷音的發生、可較寬設 定變速範圍、高效率的扭矩傳達特性，特別是，藉由變更 φ 牽引轉子90’’’的傾斜的方向，就可更集約化各零件，使裝 置可以更小型化。 第12圖及第13圖，是顯示本發明的第2觀點的無段變 速裝置的一實施例，對於前述的實施例同一的結構是附加 同一符號並省略其說明。此實施例的無段變速裝置，是如 第1 2圖及第1 3圖所示，具備：外殼1 〇、對於外殼1 〇可轉動 自如地被支撐的輸入軸20、與輸入軸20—體旋轉的載體 3 0’、對於外殻10的可轉動自如地被支撐的輸出軸40、與 輸出軸4 0 —體旋轉的太陽齒輪5 0、可轉動自如地設在輸出 -26- 200530522 (24) 軸40的周圍的作爲旋轉體的旋轉碟片11 〇、在嚙合於太陽 齒輪5 0的狀態下對於旋轉碟片1 1 0可轉動自如地被支撐且 隨著旋轉碟片11 0的旋轉可在太陽齒輪5 0的周圍公轉的複 數（3個）的遊星齒輪60、與輸入軸20—體旋轉地連結於載 體3 0’並具有嚙合於複數遊星齒輪60的內齒71"的環齒輪 70’’、與載體30’一體旋轉且朝輸入軸20的軸線L方向移動 可能地被支撐的作爲可動體的可動碟片80"、配列於可動 g 碟片80’’及旋轉碟片1 10的外周的3個牽引轉子90"(2個固定 轉子及1個可動轉子）、配置於牽引轉子90"外側的牽引環 100"等。 而且，藉由可動碟片80’’、後述旋轉碟片1 10的接觸面 112、牽引轉子90’’、牽引環100"等，構成可連續變化載 體3 0’及旋轉碟片1 10的相對旋轉速度的轉子式連續可變機 構。 輸入軸20，是如第1 2圖所示，在其端部具有板狀的凸 φ 緣2 1 ’，對於此凸緣2 1 ’，結合有略1 20度間隔配置且與軸線 L平行伸長的圓柱狀的3根銷22’。即，藉由凸緣21’及3根 銷2 2 ’，構成載體3 0 ’。 在載體30’（銷22’）中，在其先端部連結有環齒輪70"， '使環齒輪7 0 "可一體旋轉。即，輸入軸2 0旋轉的話，載體 • 3 (Γ及環齒輪70’會一體旋轉。 可動碟片80’’，是如第12圖及第13圖所示，具有可滑 動自如地外嵌於載體30’（銷22’）的3個圓孔81’’，在其外周 中，具有與牽引轉子90"的第2圓錐面92接觸的圓筒狀的接 -27- 200530522 (25) 觸面82’’。而且，可動碟片80’’，是可與輸入軸20及環齒 輪70"—體旋轉的同時，沿著銷22’朝軸線L方向往復移動 自如地被支撐。 旋轉碟片11〇，是如第12圖及第13圖所示，具有可轉 動自如地支撐3個遊星齒輪60用的3個銷1 11，可轉動自如 地外嵌（支撐）於輸出軸4 0。且，旋轉碟片1 1 0，是在其外 周，具有與牽引轉子90’’的第1圓錐面91接觸的圓錐狀的接 g 觸面1 12。 環齒輪7〇"，是具有與3個遊星齒輪60嚙合的內齒7 1 ，該3個遊星齒輪60是與太陽齒輪50嚙合，並配置於與旋 轉碟片1 10鄰接的位置。 在此裝置中，可動碟片80"的接觸面82’’是接觸於牽 引轉子90’’的第2圓錐面92，旋轉碟片1 10的接觸面1 12是接 觸於牽引轉子90’’的第1圓錐面91，進一步，將牽引轉子 90’’按壓於可動碟片80"及旋轉碟片110的方式使牽引環 φ 1〇〇"(的接觸面101’’）接觸於第1圓錐面91。 而且，可動碟片80’’是藉由朝輸入軸20的軸線L方向 移動，使接觸的第2圓錐面92上的旋轉半徑r變化，使載 體3 0’的旋轉速度（環齒輪70"的旋轉速度）及旋轉碟片1 10的 旋轉速度（遊星齒輪60的公轉速度）相對變化。即，藉由適 宜地移動可動碟片80"，對於可動碟片80’f(環齒輪70")的 旋轉速度適宜變化旋轉碟片Π 〇的旋轉速度，就可較寬範 圍地變化變速比，並可連續設定正旋轉、停止、逆旋轉。 如此，藉由採用利用牽引驅動方式轉子式的連續可變 28- 200530522 (26) 機構，就不需要習知的CVT所需要的離合器機構、反轉 •切換齒輪等，又，因爲可以同軸配置輸入軸20及輸出軸40 .，所以可以獲得··小型且便宜、空轉損失少、極力防止騷 音的發生、可較寬設定變速範圍、高效率的扭矩傳達特性 〇 第1 4圖至第1 6圖，是顯示本發明的第2觀點的無段變 速裝置的其他的實施例，對於前述的實施例同一的結構是 0 附加同一符號並省略其說明。此實施例的無段變速裝置， 是如第1 4圖至第1 6圖所示，具備：外殼1 〇、對於外殻1 〇可 轉動自地被支撐的輸入軸20、與輸入軸20—體旋轉的載體 130、對於外殼10可轉動自如地被支撐的輸出軸40、與輸 出軸4 0 —體旋轉的太陽齒輪5 0、可轉動自如地設在輸出軸 4 0的周圍的作爲旋轉體的旋轉套筒2 1 0、在嚙合於太陽齒 輪5 0狀態下對於旋轉套筒2 1 0可轉動自如地被支撐且可隨 著旋轉套筒2 1 0的旋轉而公轉於太陽齒輪5 0的周圍的複數 φ (3個）遊星齒輪60、與輸入軸20—體旋轉地連結於載體130 且具有嚙合於複數遊星齒輪60的內齒171的環齒輪170、與 旋轉套筒2 1 0 —體旋轉且朝輸出軸4 0的軸線方向l移動可 能地被支撐的作爲可動體的可動套筒1 8 0、配列於可動套 筒180及載體130(後述帽23’）的外周的3個牽引轉子190、配 • 置於牽引轉子190的外側的牽引環200等。 且，藉由：具有後述的圓筒狀的接觸面1 8丨的可動套 筒180、載體130之後述接觸面23a’、具有後述的第1圓錐 面191及第2圓錐面192的牽引轉子190、牽引環2〇〇等，構 -29- 200530522 (27) 成可連續變化載體130及旋轉套筒（旋轉體）2 10的相對旋轉 速度的方式滾動接觸的轉子式連續可變機構。 輸入軸20，是如第14圖所示，具有：在其端部形成圓 板狀的凸緣2 1 ’，可轉動自如地外嵌於旋轉套筒2 1 0的周圍 的同時與凸緣21’相面對地連結的帽23’。而且，在藉由凸 緣21’及帽23’挾持環齒輪170的狀態下藉由螺絲結合。即， 藉由凸緣21’及帽23’，構成與輸入軸20 —體旋轉的載體130 g 。因此，輸入軸20旋轉的話，載體130及環齒輪170就可一 體旋轉。 在此，在載體130的帽23’中，形成有後述的牽引轉子 190的第1圓錐面191滾動接觸的圓錐狀的接觸面23 af。 旋轉套筒210，是具有：可轉動自如地支撐3個遊星齒 輪60的3根銷211、將可動套筒180朝軸線方向L導引用的 導引溝212等，可轉動自如地外嵌（支撐）於輸出軸40。 環齒輪170，是具有與3個遊星齒輪60嚙合的內齒171 φ ，被挾持於凸緣21’及帽23’的同時藉由螺絲結合，與輸入 軸20—體旋轉。3個遊星齒輪60是與太陽齒輪50嚙合。 可動套筒180，是在其外周，具有：與牽引轉子190的 第2圓錐面1 92滾動接觸的圓筒狀的接觸面1 8 1、朝軸線方 向L伸長的導引溝182等。而且，可動套筒180，是藉由被 插入於導引溝182、2 12的球183，與旋轉套筒210—體旋轉 的同時，可滑動（往復移動）自如地被支撐於旋轉套筒2 1 0 朝輸出軸40的軸線方向L。 在此，可動套筒1 8 0，是藉由作爲推迫構件的捲簧8 3 -30- 200530522 (28) 朝一方側推迫，且藉由抵抗捲簧8 3的推迫力並移動可動套 筒180的按壓構件（不圖示），藉由在第14圖中的實線所顯 示的位置及二點鎖線所顯示位置之間移動，進行變速動作 〇 3個牽引轉子1 9 0，是與前述同樣，在各旋轉中心線S 分別與輸出軸4 0的軸線L交叉於同一點P (第3圖參照）地 傾斜的狀態下旋轉（自轉）及在預定的角度範圍公轉的方式 被支撐於保持托板195。且，3個牽引轉子190，是具有： 與成爲載體130的一部分的帽23’的接觸面23 a’接觸的第1圓 錐面191、與可動套筒180的接觸面181接觸的第2圓錐面 192、與牽引環200的凸輪面201接觸的軸承193。 且，第1圓錐面191，是在牽引轉子190的旋轉中心線 S與輸出軸40的軸線L交叉的點P(第3圖參照）具有頂點， 第2圓錐面192，是使在與可動套筒180的接觸面181接觸的 位置的母線Μ，與輸出軸40的軸線L平行。 軸承193，是可對於第1圓錐面191及第2圓錐面192相 對旋轉，並且與牽引環200的凸輪面201滾動接觸。 牽引環200，是如第14圖至第16圖所示，在軸線L方 向具有預定的厚度且輪廓是形成圓板狀，又，具有在其內 側朝周方向隔有略等間隔形成且分別內接且滾動接觸軸承 193的3個凸輪面201。而且，牽引環200，是使其中心朝徑 方向可移動自如且朝輸入軸20及輸出軸40的軸線L周圍轉 動不能地被支撐於外殼1 0。 3個凸輪面2 0 1，是在預定的領域中縮小靠近中心地按 -31 - 200530522 (29) 壓軸承1 93的負荷，在其他的預定的領域中增加靠近中心 •地按壓軸承1 9 3的負荷，即，增加法線負荷地作用。 依據此，輸出軸4 0的旋轉速度是比依據輸入軸2 0的旋 轉速度設定的値（預定値）慢時，使消解其遲延部分的方式 ，自動地增加使牽引轉子190 (的接觸面191、192)按壓接 觸面2 3 af、1 8 1的法線負荷。即，因爲隨時外加需要最小 限度的法線負荷的方式進行反饋控制，所以不會外加需要 ^ 以上的法線負荷，旋轉力就可從輸入軸20對於輸出軸40確 實傳達。 在此裝置中，可動套筒180的接觸面181是接觸於牽引 轉子190的第2圓錐面192，成爲載體130的一部分的帽23’ 的接觸面23 a’是接觸於牽引轉子190的第1圓錐面91，進一 步，使牽引轉子190按壓可動套筒180及載體130(帽23’）的 方式使牽引環200接觸軸承193。 而且，藉由使可動套筒180朝輸出軸40的軸線L方向 φ 移動，就可使接觸的第2圓錐面192上的旋轉半徑變化，使 載體130的旋轉速度（環齒輪170的旋轉速度）及旋轉套筒 2 1 0的旋轉速度（遊星齒輪60的公轉速度）相對變化。即， 藉由適宜移動可動套筒180，並適宜變化對於可動套筒 180(旋轉套筒210)的旋轉速度的環齒輪170的旋轉速度， 就可寬範圍地變化變速比，並可連續設定正旋轉、停止、 逆旋轉。且，因爲可以縮小牽引轉子190的變速比，所以 可以減少在牽引傳達領域的空轉損失，在牽引係數、傳達 效率的方面上較有利。 -32- 200530522 (30) 如此，藉由採用利用牽引驅動方式的轉子式連續可變 機構，就不需要習知的CVT所需要的及離合器機構、反 轉切換齒輪等，又，因爲可同軸配置輸入軸20及輸出軸4〇 ，且可以將牽引轉子1 9 0接近輸出軸4 0配置，所以可以獲 得：可集約化小型化零件、便宜、空轉損失少、極力防止 騷音的發生、可較寬設定變速範圍、高效率的扭矩傳達特 性。 g 在上述實施例中，轉子式連續可變機構，雖採用包含 :可動碟片80、80’、80’’或是可動套筒180、環齒輪70、 70’、170、牽引轉子 90、90’、90’，、190、牽引環 1〇〇、 100’、100’’、2 00等的結構，但是不是限定於此，只要是 利用牽引驅動方式的轉子式連續可變機構的話，可以採用 其他的機構。 在上述實施例中，牽引轉子9 0、9 (Γ、9 0 "，1 9 0的個 數雖採用3個，遊星齒輪6 0的個數雖採用3個，但不是限定 φ 於此，採用其他的個數也可以。 在上述實施例中，是太陽齒輪50、遊星齒輪60、環齒 輪70、7 0’、70"的相互關係，雖是藉由相互嚙合的齒輪傳 達扭矩，但是不限定於此，採用彼此之間相互滾動接觸來 傳達扭矩的進行牽引傳達的結構也可以。 [產業上的利用可能性] 如以上所述，本發明的無段變速裝置，因爲構造簡單 、小型且便宜、騷音等的發生被極力防止、可較寬設定變 -33- 200530522 (31) 速範圍、可傳達大的扭矩，所以當然可以適用於小排氣量 的二輪車、汽車、大排氣量的汽車等的變速裝置，對於休 旅用等的其他的車輛、或者是需要變速裝置的驅動機構等 也適用。 【圖式簡單說明】 第1圖，本發明的第1觀點的無段變速裝置的一実施形 I 態將顯示剖面圖。 第2圖，是如第1圖所示的無段變速裝置的模式圖。 第3圖，是第1圖所示無段變速裝置的一部分的模式圖 〇 第4圖A及第4圖B，是第1圖所示的無段變速裝置的 一部分的模式圖。 第5圖，是第1圖的無段變速裝置的一部分的模式圖。 第6圖A、第6圖B及第6圖C，是說明第1圖的無段變 φ 速裝置的動作的模式圖。 第7圖，是本發明的第1觀點的無段變速裝置的其他的 實施例的剖面圖。 第8圖，是本發明的第1觀點的無段變速裝置的進一步 其他的實施例的剖面圖。 第9圖，是如第8圖所示的無段變速裝置的模式圖。 第1 〇圖，是第8圖的無段變速裝置的一部分的模式圖 〇 第1 1圖，是本發明的第1觀點的無段變速裝置的進一 -34- 200530522 (32) 步其他的實施例的剖面圖。 第1 2圖，是本發明的第2觀點的無段變速裝置的一實 施例的剖面圖。 第1 3圖，是如第1 2圖所示的無段變速裝置的模式圖。 第1 4圖，是本發明的第2觀點的無段變速裝置的其他 的實施例的剖面圖。 第1 5圖，是第1 4圖的無段變速裝置的一部分的剖面圖 〇 第16圖，是如第14圖所不的無段變速裝置的模式圖。 【主要元件符號說明】 1 〇 :外殻 1 1 :外殼半體 1 1 a :軸承 1 1 b :密封件 • 1 2 :外殼半體 1 2 a :軸承 12b :密封件 12c :環狀溝 12c’ ：環狀溝 12d :銷 12e :筒狀部材 2 0 :輸入軸 2 1 :凸緣 -35- 200530522 (33) 2 Γ :凸緣 2 1 :旋轉套筒 22 :銷 2 2’ ：銷 23 :帽 23’ ：帽 23a’ ：接觸面 30 :載體 30’ ：載體 40 :輸出軸 5 0 :太陽齒輪 6 0 :遊星齒輪 70 :環齒輪 7 0 ’ ：環齒輪 70":環齒輪 71 :內齒 7 1 ":內齒 7 2 :接觸面 72’ ：接觸面 80 :碟片 8 0’’：碟片 8 0 :可動碟片 8 0 ’ ：可動碟片 80’’ ：可動碟片 -36- 200530522 (34) 8 0 :可動環 8 0 f :可動碟片 8 0’’：可動碟片 8 1 :圓孔 8 Γ ’ ：圓孔 8 2 :接觸面 82’ ：接觸面 8 2 ’ ’：接觸面 83 :捲簧 84 :按壓構件 8 5 :蝸桿 8 6 :蝸輪 8 7 :螺栓構件 90 :牽引轉子 9 0’ ：牽引轉子 90’’ ：牽引轉子 90’’’ ：牽引轉子 9 1 :第1圓錐面 9 1 ’ ：第1圓錐面 92 :第2圓錐面 92’ ：第2圓錐面 9 3 :第1連桿 9 4 ’ ：連桿 9 4 :第2連桿 -37 200530522 (35) 9 5 :彈簧 1 0 0 :牽引環 100’ ：牽引環 10 0，，：牽弓f環 100，，’··牽弓1環 1 0 1 :接觸面 1 ο Γ :接觸面 1 0 1 1 ’·接觸面 1 0 1 " ’ ：接觸面 1 1 〇 :旋轉碟片 1 1 1 :銷 1 1 2 :接觸面 130 :載體 170 :環齒輪 1 7 1 :內齒 1 8 0 :可動套筒 1 8 1 :接觸面 182 :導引溝 183 :球 190 :牽引轉子 1 9 1 :第1圓錐面 192 :第2圓錐面 1 9 3 :軸承 1 9 5 :保持托板 -38- 200530522 (36) 200 ： :牽引環 20 1 ： :凸輪面 2 10： :旋轉套筒（旋轉體） 2 11： :銷 212 ： i導引溝 • -39Surface of a movable disc; and a conical contact surface formed on the outer periphery of the ring gear; and rotatably supported around an axis inclined with respect to the axis of the input shaft or output shaft, and A two-stage conical traction rotor having a first conical surface in contact with the contact surface of the ring gear and a second conical surface in contact with the contact surface of the movable disk; and cooperating with the ring gear and the movable disk The traction ring which is inwardly in contact with the traction rotor. According to this structure, the contact surface of the movable disc will contact the second conical surface of the traction rotor g, and the contact surface of the ring gear will contact the second conical surface of the traction rotor. Further, the traction rotor will be pressed against the movable disc With the ring gear, the traction ring is brought into contact with the traction rotor (for example, the first conical surface). In addition, since the movable disc moves in the direction of the input shaft axis, the rotation radius of the second conical surface in contact will change, and the rotation speed of the carrier (revolving speed of the star gear) and the rotation speed of the ring gear will relatively change . For example, by moving the movable disc to a predetermined position, the rotation of the movable disc (carrier) is rotated together without delaying the ring gear, and it can be set to a positive rotation (for example, φ, for example, a gear ratio of 1). The ring gear rotates by a predetermined amount before it can be set to a stopped state (that is, the gear ratio is 0), and the ring gear rotation is moved by a predetermined amount before it can be set to a reverse rotation (for example, the gear ratio -0.2) The setting range of the gear ratio can be relatively wide. In the device according to the first aspect, the traction ring is disposed between a contact surface of the ring gear and a contact surface of the movable disc in an axial direction of the input shaft or output shaft. According to this structure, since the pressing force of the traction ring can press the traction rotor to the ring gear and the movable disc ′ with good balance, it can be surely obtained. -7- 200530522 (5) The traction force can be obtained to perform a more stable shifting operation. The device according to the first aspect described above includes: a pushing member that pushes the movable disc toward one side of the axis direction of the input shaft; and a device that moves and presses the movable disc against the pushing force of the pushing member. Press the component. According to this structure, the position of the movable disc can be changed by 'adjusting the position of the pressing member appropriately'. Therefore, it is easy to set a driving mechanism or the like interlocking with the pressing member inside and outside the device. In the device according to the first aspect, the first conical surface of the traction rotor has a vertex at a point where a rotation center line thereof intersects with an axis of the input shaft or the output shaft. According to this structure, the loss of idling in the contact area of the traction rotor, the ring gear, and the traction ring can be prevented, and the efficiency of the traction drive (the transmission efficiency of the traction force generated by the rolling contact) can be improved. In the device according to the first aspect, the traction ring is supported in a state where the center Φ is deviated from the axis of the input shaft or the output shaft by a predetermined amount, and is movable in the radial direction and cannot be rotated. Around the shaft edge of the input shaft or output shaft, the traction rotor is composed of a plurality of traction rotors arranged in the circumferential direction in a manner that allows the orbital rotation between the traction ring and the movable disc and ring gear. At least one of the plurality of traction rotors is supported independently of the other traction rotors. According to this structure, when the input shaft rotates, friction occurs between the movable disc (the contact surface) and the traction rotor (the second conical surface). In this case, the traction rotor that can rotate independently can be dragged to the movable disc and it is embedded between the traction ring and the movable disc by 200530522 (6). With this wedge action, the traction ring can be moved in the proper diameter direction. And the other traction rotor is screwed (strongly held) between the movable disc and the traction ring. As a result, a large traction force can be generated between the traction rotor and the ring gear, and the traction drive can be performed reliably. Further, when a load is applied to the output shaft, the rotation of the output shaft is slowed down and the ring gear is rotated. If it becomes slower, the traction g rotor that can rotate independently will move in the direction of a narrow gap, and the tightening force of other traction rotors will increase. As a result, the increase in transmission torque can eliminate the delay, and the desired transmission of torque can be performed. In the above structure, the traction rotor is composed of three traction rotors arranged in a circumferential direction between the traction ring and the movable disc and ring gear, and two of the traction rotors are rotatable. The first link is supported rotatably around the output shaft, and the remaining one of the traction rotor is rotatably supported on the second link. The first link The 2 link is rotatably provided around the aforementioned output shaft. According to this structure, the number of parts can be reduced, and stable traction driving can be ensured. In the device according to the first aspect, the traction ring is rotatably supported by the input shaft or output in a state where the center of the traction ring is coaxial with the axis of the input shaft or output shaft. Around the shaft flange of the shaft, the traction rotor includes a fixed rotor that cannot be aligned in the circumferential direction between the traction ring and the movable disc and ring gear. -9-200530522 (7) and the fixed rotor Relative movement may be supported by the movable rotor. According to this structure, when the input shaft rotates, friction occurs between the movable disc (the contact surface) and the traction rotor (the second conical surface). In this way, the traction ring will rotate and drag the movable rotor toward the movable disc, and if it is inserted between the traction ring and the movable disc, the fixed rotor is also tightened (strongly held) on the movable disc by the wedge action. Between the blade and the traction ring. As a result, a large traction force occurs, and traction driving can be performed reliably. In the above structure, the traction rotor includes: the two fixed rotors, and the movable rotor rotatably supported by the connecting rod, and the connecting rod is within a predetermined angle around the output shaft. Move freely. According to this structure, the number of parts can be reduced, and stable traction drive can be ensured. That is, if a load is applied to the output shaft, although the ring gear delays the rotation of the attracted rotor, one movable rotor moves the delayed portion in the circumferential direction and increases the tightening force of the two fixed rotors. From this φ, the increase in transmission torque can eliminate the delay and perform the desired transmission of torque. To achieve the above object, the stepless speed change device according to the second aspect of the present invention includes a carrier that rotates integrally with the input shaft, a sun gear that rotates integrally with the output shaft, and a rotatably provided around the output shaft. A rotating body, a plurality of planetary gears which are rotatably supported by the rotating body while being engaged with the sun gear, and which can revolve around the sun gear as the rotating body rotates, and are integrated with the input shaft Ring gear that is rotatably connected to the carrier and has internal teeth that mesh with the plurality of planetary gears, and a rotor that is in rolling contact with the relative rotational speed of the carrier and the rotation of the carrier continuously. 10-200530522 (8) Rotor type continuously variable mechanism. According to this structure, since a differential gear train is formed by a sun gear, a planetary gear, a ring gear, etc., a rotor-type continuously variable mechanism continuously changes a carrier that rotates integrally with the ring gear and rotates integrally with the revolution of the planetary gear. The relative rotation speed of the rotating body can transmit the rotation of the input shaft g to the output shaft in a manner that the forward rotation, the stopped state, and the reverse rotation caused by the acceleration and deceleration are continuously generated. In this way, since the clutch mechanism, the reverse switching mechanism, and the like are not required, and the input shaft and the output shaft can be arranged on the same axis, a stepless speed change device with a simple structure, a low cost, and a small size can be provided. In the device according to the second aspect, the rotor-type continuously variable mechanism includes a movable body that rotates integrally with the carrier while reciprocating in the axial direction of the input shaft and has a cylindrical contact surface on the outer periphery. And a conical contact surface formed on the outer periphery of the rotating body, and rotatably supported around an axis inclined by φ with respect to the axis of the input shaft or output shaft, and having a contact surface capable of contacting the rotating body A two-stage conical traction rotor having a first conical surface and a second conical surface that can contact the contact surface of the movable body, and a traction rotor that cooperates with the rotator and the movable body and enters the traction rotor from outside. Traction ring. According to this structure, the contact surface of the movable body will contact the second conical surface of the traction rotor, and the contact surface of the rotating body will contact the first conical surface of the traction rotor. Further, the method of making the traction rotor press the movable body and the rotating body The traction ring is brought into contact with the traction rotor (for example, the first conical surface). Furthermore, by moving the movable body in the axial direction of the input shaft, the contacting second circle -11-200530522 (9) can change the radius of rotation of the conical surface, and the rotation speed of the carrier (ring gear- The rotation speed) and the rotation speed of the rotating body (orbital speed of the planetary gear) change with respect to the ground. That is, by moving the movable body appropriately, and by appropriately changing the rotational speed of the rotary body with respect to the rotational speed of the movable body (ring gear), a wide range of gear ratios can be changed, and forward rotation, stop, and reverse rotation can be continuously set. . In the rotor-type continuously variable mechanism of the device according to the second aspect, the φ traction ring is disposed between the contact surface of the rotating body and the contact surface of the movable body in the axial direction of the input shaft or output shaft. . According to this structure, since the pressing force of the traction ring can press the traction rotor to the rotating body and the movable body with good balance, the traction force can be surely obtained and a more stable shifting operation can be performed. In the device according to the second aspect, the rotor-type continuously variable mechanism includes a unit that rotates integrally with the rotating body and reciprocates in the axial direction of the output shaft while having a cylindrical contact surface on the outer periphery. a φ movable body, a conical contact surface formed on the carrier, and a first cone that is rotatably supported around an axis inclined with respect to the axis of the input shaft or output shaft and has a contact surface with the carrier Surface and a second conical traction rotor of a second conical surface in contact with the contact surface of the movable body, and the traction ring of the traction rotor cooperates with the carrier and the movable body and comes in contact with the traction rotor. According to this structure, the contact surface of the movable body will contact the second conical surface of the traction rotor, and the contact surface of the carrier will contact the first conical surface of the traction rotor. Further, the method of pressing the traction rotor against the movable body and the rotating body Make -12-200530522 (10) the traction ring contact the traction rotor (such as a bearing). Furthermore, by moving the movable body in the axial direction of the output shaft, the rotation radius of the second conical surface in contact can be changed, and the rotation speed of the carrier (the rotation speed of the ring gear) and the rotation speed of the rotating body ( The planetary gear ’s revolution speed varies relatively. That is, by appropriately moving the movable body, the rotation speed of the rotating body is appropriately changed with respect to the rotation speed of the carrier (ring gear), the gear ratio can be changed over a wide range, and forward rotation, stop, and reverse rotation can be set continuously. In particular, because the gear ratio of the traction rotor can be reduced, the idling loss in the field of traction transmission can be reduced, and the traction coefficient and transmission efficiency can be improved. Furthermore, according to this structure, by forming the conical contact surface provided on the carrier near the output shaft, the traction rotor can be arranged near the axis of the output shaft, and the intensive parts can be achieved. Miniaturization of the device. In the rotor-type continuously variable mechanism of the device according to the second aspect, the traction ring is disposed on the contact surface of the carrier and the contact surface of the movable body in the axial direction of the input shaft or output shaft. between. According to this structure, the pressing force of the traction ring acts on the carrier and the movable body in a well-balanced manner, so that the traction force can be reliably obtained and a more stable shifting operation can be performed. The device according to the second aspect includes: a pushing member that pushes the movable body toward one side of the axial direction of the input shaft, and a pressing force that moves and presses the movable body against the pushing force of the pushing member. Member 〇 According to this structure, 'by appropriately adjusting the position of the pressing member, the position of the movable disc can be changed by -13-200530522 (11). Therefore, it is easy to set a driving mechanism or the like interlocking with the pressing member inside and outside the device. In the apparatus according to the second aspect, the first conical surface of the traction rotor has a vertex at a point where a rotation center line thereof intersects with an axis of the input shaft or the output shaft. According to this structure, the loss of idling in the contact area of the traction rotor, the ring gear, and the traction ring can be prevented, and the efficiency of the traction drive (the transmission efficiency of the traction force generated by the rolling contact) can be improved. In the device according to the second aspect, the traction ring is rotatably supported by the shaft of the input shaft or output shaft in a state where the center of the traction ring is coaxial with the axis of the input shaft or output shaft. Around the edge, the traction rotor includes a fixed rotor that cannot be aligned in the circumferential direction between the traction ring and the movable body and the rotating body, and a movable rotor that may be supported for relative movement of the fixed rotor. According to this structure, when the input shaft rotates, friction occurs between the movable disc (the contact surface) and the traction rotor (the second conical surface). In this way, the traction ring rotates and the movable rotor is dragged to the movable body, and if it is embedded between the traction ring and the movable body, the fixed rotor is also tightened (strongly held) to the movable body and the traction ring by the wedge action. between. Accordingly, a large traction force is generated, and traction driving can be performed reliably. Further, when a load is applied to the output shaft, if the rotation of the ring gear is slowed down due to the slow rotation of the output shaft, the movable rotor will move in the direction of the narrow gap, and the tightening force of other fixed rotors will increase. As a result, the increase in the transmission torque can eliminate the delay, and the desired torque transmission can be performed. -14-200530522 (12) • In the device according to the second aspect, the traction rotor includes: two fixed rotors, And one of the movable rotors rotatably supported by a connecting rod, and the connecting rod is freely movable within a predetermined angle range around the output shaft. According to this structure, the number of parts can be reduced, and stable traction drive can be ensured. That is, if a load is applied to the output shaft, although the ring gear delays the rotation of the traction rotor, one movable rotor moves the delay portion only in the circumferential direction and increases the tightening force of the two fixed rotors. As a result, the increase in transmission torque can eliminate the delay and perform the desired transmission of torque. In the device according to the second aspect, the center of the traction ring can move freely in a radial direction and cannot be supported around the axis of the input shaft or the output shaft, and has a cam surface that can be connected to the aforementioned Increasing the normal load while traction of the rotor affects the cam action; while the traction rotor may be supported in a predetermined angular range while the revolution may be supported, it has a contact shaft φ bearing which can relatively rotate the first and second conical surfaces and In contact with the aforementioned cam surface. According to this structure, because the load torque of the output shaft increases and is slower than the predetermined speed set by the rotor-type continuously variable mechanism, until the rotation delay is resolved, the bearings of the traction rotor rotate and follow the cam of the traction ring. The surface revolves within a predetermined angle range, so that the cam surface performs a camming action on the traction receiver (bearing) and automatically increases the minimum normal load required. In this way, according to the load fluctuation of the output shaft, the required normal load is feedback-controlled, stable traction is obtained, and the rotational force can be reliably transmitted -15- 200530522 (13). As described above, according to the above-mentioned stepless speed change device, a stepless speed change device can be obtained, and it is not necessary to provide a clutch mechanism, a reverse gear, a hydraulic mechanism, etc. as is conventionally known, and continuously generate positive rotation and stop caused by acceleration and deceleration The counter-rotation method conveys the rotation of the input shaft to the output shaft, and can set a wide range of speeds. It can prevent noise, etc., and can transmit large driving torque. It is small and cheap. [Embodiment] Hereinafter, the best embodiment of the present invention will be described with reference to the attached drawings. 1 to 6 are diagrams showing an embodiment of the continuously variable transmission device according to the first aspect of the present invention. Fig. 1 is a sectional view of the device, and Figs. 2 to 6 are schematic views of the device. As shown in FIG. 1, this stepless speed change device includes: a housing 10, φ, an input shaft 20 that is rotatably supported by the housing 10, and a carrier 30 that is rotatably coupled to the input shaft 20. The output shaft 40 is rotatably supported by the housing 10, the sun gear 50 which is rotatably combined with the output shaft 40, and can be rotated by the carrier 30 while being engaged with the sun gear 50. • Supported freely The three planetary gears 60, the ring 'gear 7 0' meshing with the planetary gear 60, the movable disc 80, which may be supported by the body rotating with the carrier 3 0 and moving in the axial direction of the input shaft 20, are arranged in the ring. The three traction rotors 90 on the outer periphery of the gear 70 and the movable disc 80, the traction ring 100 arranged on the outer side of the traction rotor 90, and the like. -16- 200530522 (14) Further, the relative rotation of the carrier 30 and the ring gear 70 can be continuously changed by the movable disc 80, the contact surface 72 of the ring gear 70 described later, the traction rotor 90, the traction ring 100, and the like. Rotary continuous variable mechanism of speed. The casing 10 is formed by using a mold such as an aluminum material. As shown in FIG. 1, the casing half 11 is mounted with a bearing Ua for supporting the input shaft 20 and a seal lib. The housing half 12 and the like, such as a bearing 12 a for supporting the output shaft 40 and a seal 12 b, are configured. The casing 10 is formed by coupling the casing half 11 and the casing half 12 with screws or the like, and the input shaft 20 and the output shaft 40 are rotatably supported on the same axis. As shown in FIG. 1, the input shaft 20 has a plate-shaped flange 2 1 at its end, and the flange 2 1 ′ is combined with a cylinder arranged at an interval of approximately 120 degrees and extending parallel to the axis L.状 的 3 条 针 2 2． That is, the carrier 30 is constituted by the flanges 21 and three pins 22. Each of the carriers 3 0 (pins 2 2) is rotatably supported at the tip end portion of the planetary gear 60 while maintaining engagement with the sun gear 50. That is, when the input shaft 20 rotates, the carrier 30 rotates integrally, so that the planetary gear 60 revolves around the sun gear 50 (starring movement). The ring gear 70 is shown in FIG. 1 and FIG. The inner teeth 71 of the three planetary gears 60 have a conical contact surface 72 on the outer periphery thereof that contacts a first conical surface 91 of a traction rotor 90 described below. As shown in FIG. 1, the movable disc 80 is provided with three circular holes 8 1 which are slidably fitted on the carrier 3 0 (pin 2 2) and has a traction rotor 90 on the outer periphery thereof as described below. The cylindrical contact surface 82 ° -17-200530522 (15) where the second conical surface 92 contacts is supported by the movable disc 80 reciprocatingly along the pin 22 in the direction of the axis L. The movable disc 80 is urged toward the input shaft 20 side by the coil spring 83 as a urging member, as shown in FIG. 1. On the other hand, it is arranged on the urging force side of the coil spring 83 on the opposite side. There are pressing members 84. The pressing member 84 regulates the rotating bolt member 87 while engaging with the worm 85, the worm wheel 86, and a feed-out female bolt formed on the inner periphery of the worm wheel 86, resists the urging force of the coil spring 83, and moves g in the axis L direction. Here, a drive motor for operation is connected to the upstream side of the worm 85, and is driven and controlled in accordance with an operator's operation signal. In addition, the drive mechanism of the pressing member 84 may be configured to be driven by a gear shift lever or the like provided on the outside of the casing 10. As shown in FIGS. 1 to 3 and 5, the three traction rotors 90 are rotatable in a state where each rotation center line S is inclined at the same point P crossing the axis L of the output shaft 40 ( Rotation) and revolution ground are supported. That is, two traction rotors 90 are rotatably supported by the first link 93, and the first φ rod 93 is rotatably provided around the output shaft 40. One traction rotor 90 is rotatably supported. The second link 94 is rotatably supported by the second link 94. The second link 94 is rotatably provided around the output shaft 40 independently of the first link 93, and the two traction rotors 90 can rotate independently of each other. The inclination angle of the axis L of the rotation centerline S of the traction rotor 90 can be appropriately selected according to the range of the set gear ratio. A spring 95 is provided between the first link 93 and the second link 94 so as to be able to approach each other. Here, the three traction rotors 90 are formed into large diameters, middle diameters, and small diameters with different outer diameters as shown in FIG. 5. For example, they are supported by the first link 9 3 -18- 200530522 (16) The two traction rotors 90 may have a large diameter and a middle diameter, and the one traction rotor 90 supported by the second link 94 may have a small diameter. In addition, only one trailing rotor 90 can form a smaller diameter than the other. The three traction rotors 90 are, as shown in FIGS. 1 to 3, a first conical surface having a contact surface 72 with a ring gear 70 and a contact surface ι01 of a traction ring 100 described later. 91, and a second conical surface 92 that is in contact with the contact surface 82 of the movable disc 80. g The first conical surface 91 has a vertex at a point P where the rotation center line S of the traction rotor 90 intersects with the axis L of the output shaft 40. The second conical surface 92 is a bus line µ at a position where the contact surface 82 of the movable disc 80 contacts, and is parallel to the axis L of the input shaft 20. In addition, the feature of the second conical surface 92, that is, the inclination angle of the bus line M of the rotation centerline S is based on the setting of the gear ratio, and the tilt angle of the rotation centerline S is selected by keeping the bus line M parallel to the axis L To decide. Therefore, by adopting the first conical surface 91 described above, in the contact area between the traction rotor 90 φ and the ring gear 70 and the traction ring 100, it is possible to prevent idling loss and improve the transmission efficiency of the traction force generated by the rolling contact. That is, the efficiency of the traction drive. Furthermore, the use of the second conical surface 92 allows movement between the traction rotor 90 and the movable disc 80 in the axial direction L of the movable disc 80 and allows rolling contact with each other. The traction ring 100 is a conical contact surface 101 having a conical contact surface 101 that can contact the first conical surface 91 of the traction rotor 90 as shown in FIGS. 1 to 3 and 5. The rotation center line Lf is The position is a position deviated from the axis L of the output shaft 40 by a predetermined amount. Furthermore, it is inserted into the annular groove 1 2 C of the housing half 12 and is supported by a predetermined amount of movement in the radial direction -19- 200530522 (17), while being fixed by pins 1 2 d so as not to rotate . The traction ring 100 is disposed between the movable ring 80 and the ring gear 70 in the direction of the axis L of the input shaft 20 and the output shaft 40 as shown in Figs. 1 to 3. Therefore, the pressing force of the traction ring 100 is that the first conical surface 91 and the second conical surface 92 of the traction rotor 90 press the contact surface 72 and the movable disc 80 of the ring gear 70 with good balance, respectively. Contact surface 82, it is possible to surely obtain the traction force and perform a more stable shifting operation. Here, the relationship between the three traction rotors 90 and the movable disc 80 (and the ring gear 70) will be described. First, when a certain load is applied to the output shaft 40, if the input shaft 20 and the movable disc 80 rotate, the traction rotor 90 rotates (rotates and revolves), and the ring gear 70 rotates to transmit a predetermined torque so that The output shaft 40 rotates. On the other hand, as shown in FIG. 5, in a state where the input shaft 20 and the movable disc 80 are rotated in the C 3 direction, if the load on the output shaft 40 increases, the rotation of the output shaft 40 will slow down, and the ring gear 70 will The rotation of the traction rotor 90 is delayed (C3 'direction). This delay is due to the insufficient traction torque generated by the normal load of the traction rotor 90. In addition, the smallest traction rotor 90 that can rotate independently is moved in the direction of a narrow gap (C1 direction) while rotating (rotating) in the direction of C2, and is inserted between the traction ring 100 and the movable disc 80 and the ring gear 70. Generate wedge effect. With this wedge action, the traction ring 100 will be suitable to move in the radial direction (concentric movement), and the two traction rotors 90 of the middle diameter and the large diameter are tightened more strongly -20- 200530522 (18) (strongly held ) Between the movable disc 80, the ring gear 70 and the traction ring 100, the normal load of the traction rotor 90 will increase and the traction coefficient will increase, which will increase the traction-torque. As a result, the transmission torque is increased, and the delay of the ring gear 70 is also eliminated. The three traction rotors 90 rotate together and reliably transmit the torque, and the traction drive can be performed reliably. Moreover, the traction rotor 90 is disposed on the outer periphery of the ring gear 70 and transmits 0 torque only at a position separated from the input shaft 20 and the output shaft 40 by a predetermined distance. Therefore, it can transmit large torque even in a small size. Next, the operation and principle of the above-mentioned stepless speed change device will be described with reference to FIGS. 6A to 6C. The rotation of the input shaft 20 in a predetermined direction is assumed to be a positive rotation when the output shaft 40 is rotated in the forward direction of a vehicle or the like, and a reverse rotation when the output shaft 40 is rotated in a backward direction. First, if the input shaft 20 is rotated at a predetermined speed, both the movable disc 80 and the carrier 30 will be integrated and rotated in the same direction. Furthermore, as the carrier 30 rotates, the three planetary gears 60 also rotate (rotate) and revolve at the same speed as the input shaft φ 20 in the same direction. Here, the transmission of the rotational torque from the planetary gear 60 to the sun gear 50 is based on the state change of the ring gear 70 at that time. That is, the 'ring gear 7 0' is based on: stop, rotate at the same speed as the movable disc 80 (and the input shaft 2 0), advance the movable disc 80 (rotate at a faster speed), and In any of the states such as the delayed rotation (rotation at a slower speed) of the moving disc 80, changes in the rotation speed of the sun gear 60 to the sun gear 50 and the output shaft 40 are changed. Here, by appropriately changing the position of the axial direction L of the movable disc 80 that is in contact with the second conical surface 92 of the traction rotor 90 -21-200530522 (19), the carrier 30 (and the 'movable disc 80' ) And the ring gear 70 change the relative rotation speed (rotation, slip), and can continuously change the rotation speed that is transmitted from the input shaft 20 to the output shaft 40 (forward rotation, stop, reverse rotation continuously generated with acceleration and deceleration) Rotation, etc.). That is, the difference in rotation between the ring gear 70 and the carrier 30 changes depending on the position where the movable disc 80 contacts the second conical surface 92. Therefore, the g-rotation radius of the traction rotor 90 at the intersection of the generatrical line N of the first conical surface 91 and the normal V of the movable disc 80 is R, and the second conical surface is at a position where the contact surface 82 of the movable disc 80 contacts. If the rotation radius of 92 is r, the rotation difference can be expressed as (rR) / R. If this is negative, the ring gear 70 will rotate (rapidly rotate) to the carrier 30 (and the movable disc 80) first. For example, in the state shown in FIG. 6A, r > R, the rotation of the input shaft 20 is transmitted to the output shaft 40 from a positive rotation, and the gear ratio of the movable disc 80 becomes smaller as it goes toward r 値. The movement gradually becomes smaller, as shown in FIG. 6B, when the movable disc 80 moves to r ' < R 'at a predetermined position and the ring gear φ 70 is rotated a predetermined amount with respect to the carrier 30 (movable disc 80) in advance, the gear ratio becomes 0 and the rotation of the output shaft 40 is stopped. Further, as shown in FIG. 6C, the 'movable disc 80 is moved to r 値 and further reduced to rf' ( < rf < r), the ring gear 70 rotates the carrier 30 (movable disc 80) by a predetermined amount 'in advance so that the speed ratio becomes negative and the output shaft 40 rotates in the reverse direction. Here, the movable disc 80 is a pressing member 8 4 that is appropriately moved by a driving mechanism (worm 85, worm 86, bolt member 87, etc.) against the urging force of the coil spring 83 to perform the above-mentioned shifting. action. -22- 200530522 (20) Here, for example, if the number of teeth of the sun gear 50 is 18, the number of teeth of the planetary gear 60 is 2 7 and the number of teeth of the ring gear 70 is 7 2 'for the carrier 3 0 (and movable, The rotation of the ring gear 7 0 of the disc 8) is delayed by one-fifth of the rotation so that the gear ratio becomes two. When there is no rotation delay (simultaneous rotation), the gear ratio becomes one. (Stop), the gear ratio becomes -1 (reverse rotation) when the rotation is delayed by 2/5. Because of the gear ratio of a typical car, the gear ratio is 0 (deceleration 0: infinite) when it is stopped, the gear ratio is 1.2 (deceleration ratio: 0 · 8 3 3 3) when it is overtop, and the gear ratio is reversed. It is -0.2 (reduction ratio: -5). In this case, the rotation of the ring gear 70 and the rotation of the carrier 30 are set to be "overtop" when the rotation is delayed by 1/2 5 rotations. Set to stop the gas, the first 2/5 rotation is set to back. The stepless speed change device according to the above-mentioned structure 'by adopting a continuously variable mechanism using a traction drive method, the conventional C VT and the clutch mechanism, the reverse switching gear, etc. are not needed', and the transmission φ can be arranged coaxially With the input shaft 20 and output shaft 40, it is possible to obtain: small size and low cost, low idling loss, extremely high noise prevention, wide setting speed range, and highly efficient torque transmission characteristics. FIG. 7 shows another embodiment of the continuously variable transmission according to the first aspect of the present invention. For the foregoing embodiment, changes are made to the tilting direction of the traction rotor 90 ′, the movable disc 80, and the ring gear 7. The 'and traction ring 100' are given the same reference numerals for other identical structures, and descriptions thereof are omitted. That is, the device of this embodiment is, as shown in FIG. 7, 'two traction rotors 90, and is rotatably supported by the first link 93'. One traction rotor 90 '-23- 200530522 (21) It is rotatably supported by the second link 94. -The rotation centerline V of the traction rotor 9 (Γ is arranged obliquely to intersect the axis L of the input shaft 2 0 _, and the first conical surface 9 Γ is a conical contact surface 72 ′ with the ring gear 7 0 ′. The second conical surface 92 'is in contact with the cylindrical contact surface 82' of the movable disc 80 '. The first conical surface 91' is in contact with the conical contact surface 101 of the traction ring 100 '. There is a vertex at the point where the rotation center line S 'intersects with the axis L of the input shaft 20. 0 Even with this device, continuous shifting operation can be performed in the same manner as described above, the idling loss can be suppressed, and noise can be prevented as much as possible. With a wide range of transmission speeds, high-efficiency torque transmission characteristics can be obtained. In particular, by changing the inclination direction of the traction rotor 90 ', each component can be more intensive and the device can be made smaller. The traction rotor 90' ', It is between the traction ring 100 with the contact surface 101 " and the movable disc 80 (contact surface 82) and the ring gear 70 (contact surface 72), as shown in Figs. 8 to 10, by: 2 Fixed rotor 90 '' (90a '', 90b ''), φ and 1 The rotor 90 " (90c ") is formed, the fixed rotor 90 " (90a ", 9 Ob ") is arranged in a circumferential direction and is rotatably supported on the housing half 12, while the movable rotor 90 " (90c ") is It is rotatably supported by the connecting rod 94 ', and the connecting rod 94' is movably provided in a predetermined angular range for 2 fixed rotors 90 " relative movement may be arranged around the output shaft 40-cylindrical The member 12e. Furthermore, the link 94 'is urged in a predetermined direction by the spring 95. As a result, three traction rotors 90 "are rendered incapable of revolution, and one movable rotor 90" (90c ") Is to resist the urging force of the spring 95 and relatively move the two fixed -24- 200530522 (22) rotor 90 " (90a '', 90b "). According to this device, a certain load is applied to the output shaft 40 In this case, when the input shaft 20 and the movable disc 80 are rotated, the three traction rotors 90 ″ will rotate (rotate) and rotate the ring gear 70 to transmit a predetermined torque and rotate the output shaft 40. On the one hand, as shown in FIG. 10, on the input shaft 20 In the state where the movable disc 80 is rotated in the C 3 direction, if the load on the output shaft 40 increases, the rotation of the output shaft g 4 0 becomes slower, and the ring gear 7 0 rotates (rotates) with respect to the traction rotor 9 〇 " Delay (C3 'direction). This delay is due to insufficient tractive torque generated by the traction rotor 90 " normal load. In addition, the ring gear 70 and the fixed rotor 9 0 " (9 0 a ", 9 There is a slight slip between 0 b ''). The movable rotor 9 0 f '(9 0 c' ') moves in the direction of C 2 (rotation) while moving in the direction of the narrow gap (C1 direction), and inserts traction. Wedge effect is generated between the ring 100 and the movable disc 80 and the ring gear 70. With this wedge action, the two fixed rotors 90 " (90a ,,, 90b ,,) are strongly tightened (strongly held) by φ between the movable disc 80, the ring gear 70, and the traction ring 100 " The normal load of the traction rotor 90 "will increase and the traction coefficient will increase, which increases the traction torque. As a result, the transmission torque is increased, the delay of the ring gear 70 is eliminated, and the movement (embedding) of the movable rotor 90 " (90c ") is also stopped " the torque transmission can be reliably performed " and the traction drive can be reliably performed. Furthermore, the traction rotor 90 '' is arranged on the outer periphery of the ring gear 70 and transmits torque at a predetermined distance from the input shaft 20 and the output shaft 40. Therefore, it can transmit large torque even though it is small. Moreover, in this device, the traction ring 1 00, because it only rotates and does not perform -25-200530522 (23) eccentric movement, can reduce the outer diameter size of the casing 10 of this part. -Fig. 11 is a modification of the embodiment of Figs. 8 and 9 described above: "The traction rotor 90, the tilt direction of the traction rotor 8, the movable disc 8 (V and ring gear 7 0 ', and the traction ring are changed. 1 〇〇, ", the same reference numerals are omitted for the other identical structures and the description thereof is omitted. That is, in the device of this embodiment, as shown in FIG. 11, 'traction rotor (fixed rotor and movable rotor) The 90 ° "rotation center line S 'is arranged obliquely to intersect the axis L of the input g-axis 20, and the first conical surface 91' is a conical contact surface 72 'with the ring gear 70' and the traction ring 100. The conical contact surface 101 'of "" is in contact with the second conical surface 92' and the cylindrical contact surface 82 'of the movable disc 80'. The first conical surface 91 'is at There is a vertex at the point where the rotation center line S 'intersects with the axis L of the input shaft 20. For this device, the same gear shifting operation can be performed as described above, and it is possible to achieve: suppressing idling loss, preventing the occurrence of rattle, and widening Set the transmission range, high torque transmission characteristics, especially, Changing the inclination direction of the φ traction rotor 90 '' 'makes it possible to more intensively assemble each part and make the device more compact. Figures 12 and 13 show the stepless transmission of the second aspect of the present invention. In one embodiment, the same reference numerals are omitted for the same configuration of the previous embodiment, and the description thereof is omitted. The stepless speed change device of this embodiment is provided with a casing 1 as shown in FIG. 12 and FIG. 13. For the housing 10, the input shaft 20 is rotatably supported by the input shaft 20, and the input shaft 20 is a carrier 3 0 'which is integrally rotatable, for the housing 10, the output shaft 40 is rotatably supported, and the output shaft 40 is — Rotating sun gear 50, a rotating disc 11 which is a rotating body rotatably provided around the output -26- 200530522 (24) shaft 40, and a rotating disc in a state of being engaged with the sun gear 50 A plurality of (3) planetary gears 60, which are rotatably supported by the disc 1 10 and can revolve around the sun gear 50 with the rotation of the rotating disc 110, are connected to the input shaft 20 integrally with the input shaft 20. Carrier 3 0 'with meshing teeth Ring gear 70 '' of internal tooth 71 of 60, movable disc 80 as a movable body which is integrally rotated with the carrier 30 'and moves in the direction of the axis L of the input shaft 20, and is arranged on a movable g disc 80 "and three traction rotors 90 " (2 fixed rotors and one movable rotor) on the outer periphery of the rotating disc 1 10, traction ring 100 " arranged on the outside of the traction rotor 90 " The rotor 80 ", the contact surface 112 of the rotating disc 1 10 described later, the traction rotor 90", the traction ring 100 ", etc., constitute a rotor-type continuous that can continuously change the relative rotational speed of the carrier 3 0 'and the rotating disc 1 10 Variable institutions. As shown in FIG. 12, the input shaft 20 has a plate-like convex φ edge 2 1 ′ at its end. The flange 2 1 ′ is arranged at an interval of approximately 120 degrees and extends parallel to the axis L. 3 cylindrical pins 22 '. That is, the carrier 21 is constituted by the flange 21 'and the three pins 2 2'. The carrier 30 '(pin 22') is connected to a ring gear 70 " at its tip end so that the ring gear 70 can be rotated integrally. That is, when the input shaft 20 rotates, the carrier 3 (Γ and the ring gear 70 'rotate integrally. The movable disc 80' ', as shown in Figs. 12 and 13, has a slidably fitted externally The three circular holes 81 "of the carrier 30 '(pin 22') have, on the outer periphery, a cylindrical contact with the second conical surface 92 of the traction rotor 90 " -27- 200530522 (25) contact surface 82 ". In addition, the movable disc 80" is supported by the input shaft 20 and the ring gear 70 "while being reciprocally moved along the pin 22 'in the direction of the axis L. The rotating disc 11 〇, as shown in Figs. 12 and 13, has three pins 1 11 for rotatably supporting three planetary gears 60, and can be rotatably externally embedded (supported) on the output shaft 40. The rotating disc 1 1 0 has a conical contact surface 1 12 on its outer periphery that contacts the first conical surface 91 of the traction rotor 90 ″. The ring gear 70 and “3” The internal teeth 7 1 of the gear 60 mesh with each other. The three planetary gears 60 mesh with the sun gear 50 and are disposed adjacent to the rotating disc 1 10. In this device, the contact surface 82 "of the movable disk 80" is in contact with the second conical surface 92 of the traction rotor 90 ", and the contact surface 1 12 of the rotating disk 1 10 is in contact with the traction rotor 90" The first conical surface 91 further presses the traction rotor 90 '' against the movable disc 80 " and the rotating disc 110 so that the traction ring φ 100 and (the contact surface 101 ") contacts the first cone Surface 91. Furthermore, by moving the movable disc 80 "in the direction of the axis L of the input shaft 20, the rotation radius r on the second conical surface 92 that is in contact is changed, so that the rotation speed of the carrier 3 0 '(ring gear The rotation speed of 70 ") and the rotation speed of the rotating disc 1 (revolving speed of the planetary gear 60) are relatively changed. That is, by appropriately moving the movable disc 80 ", the movable disc 80'f (ring gear 70 ";) The rotation speed is suitable to change the rotation speed of the rotating disc Π 〇, so that the gear ratio can be changed in a wide range, and the forward rotation, stop, and reverse rotation can be set continuously. In this way, by using a traction drive method, the rotor type Continuously variable 28- 200530522 (26) It eliminates the need for the clutch mechanism, reverse gear, and gears required for the conventional CVT. In addition, the input shaft 20 and the output shaft 40 can be arranged coaxially. Therefore, it is possible to obtain a compact, inexpensive, low idling loss, Trying to prevent the occurrence of noise, wide setting of the shift range, and high torque transmission characteristics. Figures 14 to 16 are other embodiments of the stepless speed change device showing the second aspect of the present invention. In the foregoing embodiment, the same configuration is 0, and the same reference numerals are attached, and descriptions thereof are omitted. As shown in FIGS. 14 to 16, the stepless speed change device of this embodiment includes a housing 10, an input shaft 20 that is rotatably supported by the housing 10, and an input shaft 20— A carrier 130 for body rotation, an output shaft 40 rotatably supported by the casing 10, and a sun gear 50 for body rotation, and a rotation body rotatably provided around the output shaft 40 The rotating sleeve 2 1 0 is rotatably supported on the rotating sleeve 2 10 while being engaged with the sun gear 50, and can be revolved in the sun gear 5 0 as the rotating sleeve 2 1 0 rotates. The surrounding plural φ (three) planetary gears 60, a ring gear 170 rotatably connected to the carrier 130 with the input shaft 20 and having internal teeth 171 that mesh with the plural planetary gears 60, and a rotating sleeve 2 1 0 -body The three traction rotors that are supported by the movable sleeve 180, which is a movable body, which can rotate and move in the axial direction l of the output shaft 40, are arranged on the outer periphery of the movable sleeve 180 and the carrier 130 (the cap 23 'described later). 190. A traction ring 200 provided on the outside of the traction rotor 190 and the like. In addition, a movable sleeve 180 having a cylindrical contact surface 1 丨 described later, a carrier 130 contact surface 23 a ′ described later, and a traction rotor 190 having a first conical surface 191 and a second conical surface 192 described later. , Traction ring 2000, etc., structure -29- 200530522 (27) into a rotor-type continuous variable mechanism that can continuously change the relative rotational speed of the carrier 130 and the rotating sleeve (rotating body) 2-10. As shown in FIG. 14, the input shaft 20 includes a flange 2 1 ′ having a disc shape at an end portion thereof, and is rotatably fitted around the rotary sleeve 2 1 0 while being fitted with the flange 21. 'Cap 23 connected face to face'. Then, the ring gear 170 is held by the flange 21 'and the cap 23' by the screw. That is, the flange 21 'and the cap 23' constitute a carrier 130 g that rotates integrally with the input shaft 20. Therefore, when the input shaft 20 is rotated, the carrier 130 and the ring gear 170 can be rotated together. Here, the cap 23 'of the carrier 130 is formed with a conical contact surface 23 af of a first conical surface 191 of a traction rotor 190 described later in rolling contact. The rotating sleeve 210 is provided with three pins 211 that rotatably support the three star gears 60, a guide groove 212 that guides the movable sleeve 180 in the axial direction L, and the like, and can be rotatably fitted outside (support ) On the output shaft 40. The ring gear 170 has internal teeth 171 φ meshing with the three planetary gears 60 and is held by the flange 21 'and the cap 23' while being screwed together to rotate integrally with the input shaft 20. The three planetary gears 60 mesh with the sun gear 50. The movable sleeve 180 has, on its outer periphery, a cylindrical contact surface 1 8 in rolling contact with the second conical surface 1 92 of the traction rotor 190, a guide groove 182 extending in the axial direction L, and the like. The movable sleeve 180 is supported by the rotating sleeve 2 while being slidable (reciprocating) by a ball 183 inserted into the guide grooves 182, 2 and 12 while rotating integrally with the rotating sleeve 210. 1 0 Towards the axial direction L of the output shaft 40. Here, the movable sleeve 1 8 0 is pushed to one side by the coil spring 8 3 -30- 200530522 (28) as a pushing member, and moves the movable sleeve by resisting the pushing force of the coil spring 8 3. The pressing member (not shown) of the cylinder 180 moves between the position shown by the solid line in FIG. 14 and the position shown by the two-point lock line to perform a variable speed operation. 3 traction rotors 190, and In the same manner as described above, each of the rotation centerlines S is supported in such a manner that it rotates (rotates) and revolves within a predetermined angle range while being inclined while crossing the axis L of the output shaft 40 at the same point P (refer to FIG. 3). Hold the pallet 195. The three traction rotors 190 include a first conical surface 191 in contact with the contact surface 23 a ′ of the cap 23 ′ which is a part of the carrier 130, and a second conical surface in contact with the contact surface 181 of the movable sleeve 180. 192. A bearing 193 in contact with the cam surface 201 of the traction ring 200. The first conical surface 191 has a vertex at a point P (refer to FIG. 3) at which the rotation center line S of the traction rotor 190 intersects with the axis L of the output shaft 40, and the second conical surface 192 is formed on the movable sleeve. The generatrical line M at the position where the contact surface 181 of the cylinder 180 contacts is parallel to the axis L of the output shaft 40. The bearing 193 is rotatable relative to the first conical surface 191 and the second conical surface 192, and is in rolling contact with the cam surface 201 of the traction ring 200. The traction ring 200 has a predetermined thickness in the axis L direction as shown in Figs. 14 to 16 and has a circular plate shape. The traction ring 200 is formed at equal intervals in the circumferential direction on the inner side of the traction ring 200. Then, the three cam surfaces 201 of the bearing 193 are in rolling contact. Moreover, the traction ring 200 is supported by the casing 10 so that its center can move freely in the radial direction, and can rotate around the axis L of the input shaft 20 and the output shaft 40. The three cam surfaces 2 0 1 reduce the load near the center in the predetermined area by pressing -31-200530522 (29) The load of the bearing 1 93 is increased, and in the other predetermined areas the load near the center is increased by 1 9 3 Load, that is, increasing the normal load. Based on this, when the rotation speed of the output shaft 40 is slower than 値 (predetermined 値) set according to the rotation speed of the input shaft 20, the delay portion is eliminated, and the contact surface 191 of the traction rotor 190 is automatically increased. , 192) Press the normal load on the contact surfaces 2 3 af, 1 8 1. In other words, since feedback control is performed in a manner that requires a minimum normal load at any time, the rotation force can be reliably transmitted from the input shaft 20 to the output shaft 40 without applying a normal load more than ^. In this device, the contact surface 181 of the movable sleeve 180 is a second conical surface 192 that is in contact with the traction rotor 190, and the contact surface 23 a ′ of the cap 23 ′ that is a part of the carrier 130 is the first contact with the traction rotor 190. The conical surface 91 further brings the traction ring 200 into contact with the bearing 193 so that the traction rotor 190 presses the movable sleeve 180 and the carrier 130 (the cap 23 '). Furthermore, by moving the movable sleeve 180 in the axis L direction φ of the output shaft 40, the rotation radius of the second conical surface 192 in contact can be changed, and the rotation speed of the carrier 130 (the rotation speed of the ring gear 170) can be changed. And the rotation speed of the rotary sleeve 2 10 (the revolution speed of the planetary gear 60) is relatively changed. That is, by appropriately moving the movable sleeve 180 and appropriately changing the rotational speed of the ring gear 170 with respect to the rotational speed of the movable sleeve 180 (rotating sleeve 210), the gear ratio can be changed in a wide range, and the positive ratio can be continuously set. Rotate, stop, reverse. Furthermore, since the gear ratio of the traction rotor 190 can be reduced, the idling loss in the traction transmission field can be reduced, which is advantageous in terms of traction coefficient and transmission efficiency. -32- 200530522 (30) In this way, by adopting a rotor-type continuously variable mechanism using a traction drive method, the conventional CVT and the clutch mechanism, the reverse switching gear, etc. are not needed, and because it can be arranged coaxially The input shaft 20 and the output shaft 40, and the traction rotor 190 can be arranged close to the output shaft 40, so it can be obtained: intensive and compact parts, cheap, low idling loss, as much as possible to prevent noise, can be compared Wide transmission speed range and high torque transmission characteristics. g In the above embodiments, although the rotor-type continuously variable mechanism includes: a movable disc 80, 80 ', 80' 'or a movable sleeve 180, a ring gear 70, 70', 170, and a traction rotor 90, 90 ', 90', 190, traction ring 100, 100 ', 100' ', 200, etc., but it is not limited to this, as long as it is a rotor type continuously variable mechanism using a traction drive method, it can be used Other agencies. In the above embodiment, although the number of traction rotors 90, 9 (Γ, 9 0 ", 190 is three, and the number of planetary gear 60 is three, it is not limited to φ, Other numbers may be used. In the above embodiment, the sun gear 50, the planetary gear 60, the ring gear 70, 70 ', 70 " are related to each other, although the torque is transmitted through the gears that mesh with each other, but not Limited to this, it is also possible to use a traction transmission structure that uses rolling contact with each other to transmit torque. [Industrial Applicability] As described above, the stepless transmission of the present invention has a simple structure, a small size, and Low cost, noise, etc. are prevented as much as possible, and wide settings can be changed -33- 200530522 (31) Speed range and large torque can be transmitted, so of course it can be applied to two-wheelers, automobiles, and large displacements with small displacements Transmissions such as automobiles are also applicable to other vehicles such as recreational vehicles or drive mechanisms that require a transmission. [Brief Description of the Drawings] Fig. 1 is a stepless transmission of the first aspect of the present invention. Yi Section I will show a sectional view. Figure 2 is a schematic view of the stepless transmission shown in Figure 1. Figure 3 is a schematic view of a part of the stepless transmission shown in Figure 1. 4 A and 4B are schematic diagrams of a part of the continuously variable transmission shown in Fig. 1. Fig. 5 is a schematic diagram of a part of the continuously variable transmission shown in Fig. 1. Figs. 6B and 6C are schematic diagrams illustrating the operation of the stepless variable speed device of Fig. 1. Fig. 7 is a sectional view of another embodiment of the stepless speed changing device according to the first aspect of the present invention. Fig. 8 is a sectional view of still another embodiment of the continuously variable transmission according to the first aspect of the present invention. Fig. 9 is a schematic diagram of the continuously variable transmission shown in Fig. 8. 1 〇 FIG. 8 is a schematic view of a part of the continuously variable transmission of FIG. 8. FIG. 11 is a step-34- 200530522 (32) of another embodiment of the continuously variable transmission of the first aspect of the present invention. Sectional view. Fig. 12 is a sectional view of an embodiment of the continuously variable transmission according to the second aspect of the present invention. Fig. 13 is a view such as Fig. 12 is a schematic view of the stepless transmission device shown in Fig. 12. Fig. 14 is a sectional view of another embodiment of the stepless transmission device according to the second aspect of the present invention. Fig. 15 is a view showing Fig. 14 A sectional view of a part of the stepless speed change device. FIG. 16 is a schematic view of the stepless speed change device as shown in FIG. 14. [Description of main component symbols] 1: Shell 1 1: Shell half 1 1 a: bearing 1 1 b: seal • 1 2: housing half 1 2 a: bearing 12b: seal 12c: annular groove 12c ': annular groove 12d: pin 12e: cylindrical member 2 0: input shaft 2 1: flange-35- 200530522 (33) 2 Γ: flange 2 1: rotary sleeve 22: pin 2 2 ': pin 23: cap 23': cap 23a ': contact surface 30: carrier 30': carrier 40 : Output shaft 5 0: sun gear 6 0: planetary gear 70: ring gear 7 0 ′: ring gear 70 ": ring gear 71: internal gear 7 1 ": internal gear 7 2: contact surface 72 ': contact surface 80 : Disc 8 0 '': Disc 8 0: Movable Disc 80 0 ′: Movable Disc 80 '': Movable Disc-36- 200530522 (34) 8 0: Movable Ring 8 0 f: Movable Disc 8 0 '': movable Disc 8 1: round hole 8 Γ ': round hole 8 2: contact surface 82': contact surface 8 2 ′ ': contact surface 83: coil spring 84: pressing member 8 5: worm 8 6: worm gear 8 7: bolt Component 90: Traction rotor 90 0 ': Traction rotor 90' ': Traction rotor 90' '': Traction rotor 9 1: First conical surface 9 1 ': First conical surface 92: Second conical surface 92': Second Conical surface 9 3: 1st link 9 4 ′: link 9 4: 2nd link -37 200530522 (35) 9 5: spring 1 0 0: traction ring 100 ′: traction ring 10 0, :: pull bow f-ring 100, '... pull bow 1 ring 1 0 1: contact surface 1 ο Γ: contact surface 1 0 1 1' · contact surface 1 0 1 " ': contact surface 1 1 〇: rotating disc 1 1 1: Pin 1 1 2: Contact surface 130: Carrier 170: Ring gear 1 7 1: Internal tooth 1 8 0: Movable sleeve 1 8 1: Contact surface 182: Guide groove 183: Ball 190: Traction rotor 1 9 1 : 1st conical surface 192: 2nd conical surface 1 9 3: bearing 1 9 5: holding plate -38- 200530522 (36) 200:: traction ring 20 1:: cam surface 2 10:: rotary sleeve (rotating Body) 2 11:: Pin 212: i guide groove • -39