JPH1089435A - Continuously variable transmission - Google Patents

Continuously variable transmission

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Publication number
JPH1089435A
JPH1089435A JP27517596A JP27517596A JPH1089435A JP H1089435 A JPH1089435 A JP H1089435A JP 27517596 A JP27517596 A JP 27517596A JP 27517596 A JP27517596 A JP 27517596A JP H1089435 A JPH1089435 A JP H1089435A
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JP
Japan
Prior art keywords
ball rolling
shaft
driven
driving shaft
rolling elements
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP27517596A
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Japanese (ja)
Inventor
Mamoru Ishikuri
衛 石栗
Original Assignee
Mamoru Ishikuri
衛 石栗
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by Mamoru Ishikuri, 衛 石栗 filed Critical Mamoru Ishikuri
Priority to JP27517596A priority Critical patent/JPH1089435A/en
Publication of JPH1089435A publication Critical patent/JPH1089435A/en
Application status is Pending legal-status Critical

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Abstract

PROBLEM TO BE SOLVED: To enable the transmission to rotate a driven shaft forward, stop and rotate reversely in keeping a driving shaft rotate intact, and carry out transmission of its turning force compact and excellent in accuracy via plurality of ball rolling elements. SOLUTION: A driving shaft 2 and a driven shaft 3 set up on the same axis are pivoted to both sides of a casing 1. A driven wheel 4 is installed in an end of the driven shaft 3 via a torque cam 5, while a bearing ring 6 opposed to this driven wheel 4 is locked to the casing 1. Subsequently, four ball rolling elements 8, 8, 8 and 8 equipped with outer ring 9 engaging and contacting with pressure at one point on a spherical surface are planetarily set up in an interval between the bearing ring 6 and the driven wheel 4. In addition, a forked driving carrier 14 rotating as holding these ball rolling elements 8, 8, 8 and 8 regular intervals is installed in the driving shaft 2, and then a shifter 12, tilting all the ball rolling elements 8, 8, 8 and 8 simultaneously via a rocking member 11 having a woodruff keyway 10 engaged with the outer ring 9 of the ball rolling element 8, is installed on the driving shaft free of sliding motion.

Description

【発明の詳細な説明】 DETAILED DESCRIPTION OF THE INVENTION

【0001】 [0001]

【発明の属する技術分野】本発明は回転力の伝達に複数のボール転動子を介して行う無段変速装置に関するものである。 The present invention relates to relates to a continuously variable transmission performed via a plurality of balls rolling elements in the transmission of rotational force.

【0002】 [0002]

【従来の技術】回転力の伝達にボール転動子を介して行う無段変速装置として特公昭38−25315号公報や実公昭39−18631号公報等種々の発明、考案がなされているが、原動軸を回転させたまゝ従動軸を正逆転させたり停止させることができる無段変速装置は知られていない。 BACKGROUND ART Japanese Patent Publication 38-25315 discloses and Japanese Utility Model 39-18631 Patent Publication various inventions to the transmission of the rotational force as a continuously variable transmission performed via the ball rolling element, but devised have been made, continuously variable transmission can be stopped or to forward reverse or ゝ driven shaft which rotates the driving shaft is not known.

【0003】 [0003]

【発明が解決しようとする課題】本発明は、原動軸を回転させたまゝ、従動軸を正転、停止、逆転させることができ、しかも、小型で精度がよい回転力の伝達に複数のボール転動子を介して行う無段変速装置を提供することを課題とするものである。 The present invention 0005] is, Mama rotating the driving shaft, forward of the driven shaft, stop, can be reversed, Moreover, a plurality of ball transfer accuracy good rotational force in a small it is an object of the present invention to provide a continuously variable transmission performed through the rolling elements.

【0004】 [0004]

【課題を解決するための手段】本発明は上記の課題を解決するためになされたもので、ケーシングの両側に、同一軸線上に配置した原動軸と従動軸を枢着し、この従動軸の端部にトルクカムを介して従動車を設けると共に、 The present invention SUMMARY OF] has been made to solve the above problems, on both sides of the casing, pivotally mounted a driving shaft and a driven shaft disposed in the same axis, the driven shaft provided with a driven wheel via a torque cam on the end,
この従動車と対向させた軌道リングを前記ケーシングに固定し、この軌道リングと前記従動車間にそれぞれ球面上の一点において圧接係合する適数の外輪付ボール転動子を遊星状に配置し、これらボール転動子を一定間隔を保持し乍ら回動するフオーク状の原動キャリアを原動軸に設け、つ前記ボール転動子の外輪に半月溝を係合させた揺動部材を介して全ボール転動子を同時に傾斜させるシフターを原動軸上に摺動自在に設けたものである。 This driven wheel and the counter is allowed orbit ring fixed to the casing, placing the ball rolling members with appropriate number of the outer ring for pressing engagement at one point on each the track ring and the driven vehicle spherical planetary shape, the fork-like driving carrier for these ball rolling members retained 乍Ra rotated a predetermined distance provided in the driving shaft, one through said rocking member crescent groove engaged with the outer ring of the ball rolling members total the shifter to tilt the ball rolling members simultaneously in which slidably disposed on the driving shaft.

【0005】 [0005]

【作用】原動軸を回動させると、各外輪付ボール転動子は、原動キャリアを介して遊星回転すると共に、外輪両側球面が軌道リングと従動車に接しているため公転する。 [Action] rotates the driving shaft, the ball rolling elements with each outer ring, as well as the planet rotated via the driving carrier, the outer ring on both sides spherical revolves because of contact with the track ring and the driven wheel. そして、シフターが中間位置にある時は従動軸は停止しているが、シフターを従動軸方向にシフトすると従動軸は正転し、逆方向にシフトすると従動軸は逆転する。 Then, although when the shifter is in the intermediate position is stopped driven shaft, the driven shaft when shifting the shifter to the driven shaft direction is forward, the driven shaft when the shift in the opposite direction is reversed.

【0006】 [0006]

【発明の実施の形態】図1〜図3は本発明の第1の実施例を示すもので、図1は縦断側面図、図2は図1のA− 1-3 DETAILED DESCRIPTION OF THE INVENTION show a first embodiment of the present invention, FIG. 1 is a vertical sectional side view, FIG. 2 in FIG. 1 A-
A線断面図、図3は分解斜視図である。 A line cross-sectional view, FIG. 3 is an exploded perspective view.

【0007】図1〜図3において、1は両側に原動軸2 [0007] 1 to 3, 1 is the driving shaft on both sides 2
と従動軸3を同一軸線上に枢着したケーシング、4はトルクカム5を介して前記従動軸3の内側端に取付けた従動車、6は前記従動車4と対向してケーシング1内に止ビス7で固定した軌道リングである。 Casing the driven shaft 3 and pivotally mounted on the same axis line and, 4 driven wheel attached to the inner end of the driven shaft 3 through the torque cam 5, 6 stop in the casing 1 to face the driven wheel 4 bis 7 is a fixed orbit ring.

【0008】8は前記従動車4と軌道リング6間にそれぞれ球面上の一点において圧接係合する外輪9を備えたボール転動子で、この実施例では図1に示すように遊星状に4個のボール転動子が等間隔に配置されている。 [0008] 8 4 the ball rolling members having a outer ring 9 for pressing engagement at each one point on the spherical surface between the driven wheel 4 and the raceway ring 6, in this embodiment the planetary shape as shown in FIG. 1 number of balls rolling elements are arranged at regular intervals.

【0009】そうして、これらのボール転動子8、8, [0009] Then, these ball rolling element 8, 8,
8,8は、それぞれ外輪9を半月溝10に係合させた揺動部材11を介して、原動軸2上を横動自在に設けたシフター12のコ状の凹部13に支承されていて、シフター12を横動させると各ボール転動子8は左右に傾斜させられるようになっている。 8, 8 via the rocking member 11 engaging the outer ring 9 in half moon groove 10, respectively, have been supported on the driving shaft 2 in a U-shaped recess 13 of the shifter 12 which is provided freely traverses, each ball and the shifter 12 is horizontally moved rolling elements 8 are adapted to be tilted to the left and right.

【0010】そして、これらボール転動子8,8,8, [0010] Then, these ball rolling elements 8,8,8,
8の外輪9,9,9,9は、原動軸2の内側端に固定されたフオーク状の原動キャリア14の爪片14aと当接していて、原動軸2が回転すると、シフター12と共に原動軸2の周囲を公転し乍ら遊星回転するように構成されている。 8 the outer race of 9,9,9,9 is in contact with the claw piece 14a of the driving shaft 2 of the fork-like driving carrier 14 which is fixed to the inner end those, when the driving shaft 2 is rotated, the driving shaft with shifter 12 revolving around the 2 is configured to 乍Ra planet rotates.

【0011】この第1の実施例では、ボール転動子8に回動自在に取付けたベアリング状の外輪9は、図2に示されるように、ボールベアリングと同様ボールを介して外輪9をボール転動子本体に取付けるようにしたが、図4の(a)のように外輪9に軌道溝91を設け、その軌道溝91に円筒コロ92を係合させるようにしたボール転動子、図4の(b)のように、ボール転動子本体に軌道溝93を設け、この軌道溝93に円筒コロ92を係合させるようにしたボール転動子、図4の(c)のように鼓型コロ94を外輪9とボール転動子本体間に設けるもの、あるいは図4の(d)のようにボールベアリング9 [0011] In the first embodiment, the bearing-shaped outer ring 9 mounted rotatably on the ball rolling element 8, as shown in FIG. 2, the ball outer ring 9 through a ball bearing similar to the ball rolling element was to be mounted on the body, the ball rolling elements, drawing and so as to the outer ring 9 of the raceway groove 91 provided, engaging the cylindrical roller 92 to the raceway grooves 91 as in FIG. 4 (a) as in the fourth (b), the raceway grooves 93 provided in the ball rolling element body, the ball rolling elements in which the cylindrical rollers 92 in this raceway groove 93 so as to engage, as shown in FIG. 4 (c) ball bearings such as those provided hourglass roller 94 between the outer ring 9 and the ball rolling element body, or in FIG. 4 (d) 9
5を外輪に使い、ボール転動子本体を半球合体形式としたものを使用することも出来る。 5 to use the outer ring, the ball rolling element body can also be used after a hemisphere united format. これらのボール転動子は従来のボールベアリング製造技術を使って製作精度の高いものが得られる。 These ball rolling element is having a high fabrication accuracy is obtained by using a conventional ball bearing manufacturing technology.

【0012】シフター12はボールベアリング15を介して外周にラックの機能を持たせるための多条突条16 [0012] The shifter 12 is multi-threaded protrusion 16 of the order to have the rack of the function on the outer periphery through a ball bearing 15
を設けたシフトドラム17と連繋されていて、ピニオン18を前記多条突条16に噛合させた変速軸19を介して微動ハンドル装置20により原動軸2上を軸方向に横動するようになっている。 The optionally be cooperative with the shift drum 17 which is provided, adapted traverses the upper driving shaft 2 in the axial direction by the fine control handle 20 to the pinion 18 via the transmission shaft 19 which is engaged with the multiple thread protrusions 16 ing.

【0013】微動ハンドル装置20は差動歯車減速機構から成り、即ちケーシング1に固定された固定冠歯車2 [0013] fine control handle 20 comprises a differential gear reduction mechanism, i.e., the fixed crown gear 2 fixed to the casing 1
01と、変速軸19に固定され固定冠歯車201に噛合する可撓性冠歯車202と、ハンドル21を備え、2個のボール203,203を前記可撓性冠歯車202に押圧し乍ら移動させる原動円板204から構成されていて、その動作について説明すれば次の通りである。 01, the flexible crown gear 202 which is fixed to the gear shaft 19 meshes with a fixed crown wheel 201, provided with a handle 21, pressed 乍Ra move two balls 203, 203 to the flexible crown wheel 202 it is composed of the driving disc 204 to be, which will be described as follows for the operation.

【0014】図5は微動ハンドル装置20の動作説明のための展開図で、今、ハンドル21を持って原動円板2 [0014] Figure 5 is a developed view for explaining the operation of the fine control handle 20, now driving disc with a handle 21 2
04をP1矢方向へ回転させると、ボール203はP2 04 is rotated to P1 arrow direction, the ball 203 is P2
方向へ自転しつつ公転すると共に、可撓性冠歯車202 Together rotate and revolve in the direction, the flexible crown wheel 202
に波状運動を発生させ、その歯を固定冠歯車201の歯に順次噛合せつつP3方向へ進む事になり、従って、可撓性冠歯車202は固定冠歯車201との歯数差だけ差動減速する。 To generate a wave like motion, while sequentially mesh with the teeth on the teeth of the fixed crown wheel 201 will be proceed to P3 direction, therefore, the flexible crown wheel 202 is only difference in the number of teeth and the fixed crown wheel 201 Differential to slow down.

【0015】以上のように構成されるので、ハンドル2 [0015] Since the configurations as described above, the handle 2
1を回動すると、変速軸19が回動し、ピニオン18、 When 1 is rotated, the shift shaft 19 is rotated, the pinion 18,
それと噛合する多条突条16を備えたシフトドラム1 At the same shift drum 1 having a multiple-thread ridge 16 which meshes
7、ボールベアリング15及びシフター12を介して各ボール転動子8、8,8,8を同時に揺動せしめる。 7, allowed to simultaneously swing the ball rolling members 8,8,8,8 via the ball bearings 15 and shifter 12.

【0016】そしてボール転動子8が揺動せしめられると、ボール転動子と接触する従動車4側の回転有効径と軌道リング6側の回転有効径が相対的に変化するため、 [0016] When the ball rolling members 8 are swung, the rotation effective diameter of rotation effective diameter and the track ring 6 side of the driven wheel 4 side in contact with the ball rolling elements is relatively changed,
図6に示すように従動車14、つまり従動軸3の回転が変化する。 Driven wheel 14 as shown in FIG. 6, that is the rotation of the driven shaft 3 is changed.

【0017】図6はボール転動子8,8,8,8が揺動した時の軌道リング6及び従動車4との接触状態を示すもので、〔I〕の状態ではボール転動子と接触する軌道リング6側の回転有効径cの方が従動車4側の回転有効径bよりも大きいので、従動車4は原動軸2と同じ方向に回転すると共に高速で回転する。 [0017] FIG. 6 shows the state of contact between the raceway ring 6 and the driven wheel 4 when the ball rolling elements 8,8,8,8 swings, and the ball rolling elements are in the form of [I] since towards rotating effective diameter c of the contact raceway ring 6 side is greater than the rotational effective diameter b of the driven wheel 4 side, the driven wheel 4 is rotated at a high speed while rotating in the same direction as the driving shaft 2. そしてシフター12 And shifter 12
を右方にシフトすると無段で回転速度が低下し、〔I It reduces the rotational speed of a shift to the continuously variable to the right, [I
I〕の中間位置の状態になると両回転有効径のbとcが同一となるので、ボール転動子は公転し乍ら遊星回転するが、従動車4は停止する。 Since b and c of the two rotary effective diameter and a state of the intermediate position I] are the same, the ball rolling element is rotated revolve and 乍Ra planet follower wheel 4 is stopped. そして更に右方へ移動させると、軌道リング6側の回転有効径cの方が従動車4側の回転有効径bよりも小さくなるので従動車4は逆転し、〔III〕の状態では最高速になる。 When the moved further to the right, since the direction of rotation effective diameter c of the raceway ring 6 side becomes smaller than the rotation effective diameter b of the driven wheel 4 side driven wheel 4 is reversed, the highest speed in the state of (III) become. なお、図6において斜線を付した部分はケーシング1に固定されている部分を示している。 The portion hatched in FIG. 6 shows a part fixed to the casing 1.

【0018】こゝで軌道リング6と圧接するボール転動子8の回転有効径をb. [0018] In this ゝ the rotation effective diameter of the orbit ring 6 and the pressure to the ball rolling elements 8 b. 従働車4と圧接するボール転動子8の回転有効径c,従働車4の回転有効径をd,軌道リング6の有効径をfとすれば、変速比Vは次式で表わされる。 Rotation effective diameter c of 従働 wheel 4 and pressed against ball rolling element 8, the rotation effective diameter of 従働 wheel 4 d, if the effective diameter of the raceway ring 6 is f, the gear ratio V is expressed by the following equation .

【0019】 [0019]

【数1】 [Number 1]

【0020】図7は原動軸2が起動開始した時の4個のボール転動子8,8、8,8と揺動部材11,11,1 [0020] Figure 7 is four ball rolling members 8,8,8,8 and the swinging member when the driving shaft 2 is started started 11,11,1
1,11の動きを示すもので、(a)図の起動前の状態では、従働車4及び軌道リング6に対するそれらの位置はバラバラであるが、原動軸2が起動すると、トルクカム5の作用により、従働車4とボール転動子12、ボール転動子12と起動リング6の接触圧が高まり、フローテイング状態にあった4個のボール転動個8と揺動部材11は(b)図の調心状態になる。 Shows the movement of the 1 and 11, in the pre-startup state of the (a) diagram, the position thereof relative to 従働 wheel 4 and orbital ring 6 is a disjointed, the driving shaft 2 is started, the action of the torque cam 5 Accordingly, 従働 wheel 4 and the ball rolling elements 12 increases the contact pressure between the ball rolling members 12 start ring 6, four balls Utatedoko 8 and the swing member 11 that has been in a floating state (b ) made in aligning state of view.

【0021】そして、図1において、ハンドル21を回動すると、変速軸19に設けたピニオン18、それと噛合する多条突条16、シフトドラム17及びボールベアリング15を介してシフター12が軸方向に横動し、各揺動部材11を介して凹部13と係合する外輪9を介してボール転動子8の回転軸を揺動せしめる。 [0021] Then, in FIG. 1, when turning the handle 21, the pinion 18 provided on the transmission shaft 19, the same multi-start protrusions 16 which meshes, shifter 12 via a shift drum 17 and the ball bearing 15 in the axial direction and traverses, allowed to swing spindle of the ball rolling element 8 through the outer ring 9 which engages with the recess 13 via the respective swing members 11.

【0022】すなわち、ハンドル21を回動することにより、原動軸2を回転させたまゝ従動軸3を正転の高速回転から無段階に低速回転に移行させた後停止させ、更にハンドル21を回動することにより、今度は従動軸3 [0022] That is, by turning the handle 21 is stopped after being shifted to the lower speed rotation steplessly driving shaft 2 or ゝ driven shaft 3 which is rotated from the high speed rotation of the forward rotation, further a handle 21 times by dynamic, in turn, driven shaft 3
を逆転させた後無段階に高速回転に移行させることができるものである。 In which it can be shifted to the high speed steplessly after reversed.

【0023】図8〜図10はボール転動子の数を5個とし、且つ別の傾斜機構によってボール転動子を傾斜させるようにした第2の実施例を示すもので、図8は縦断側面図、図9はそのB−B線断面図、図10はシフターと揺動部材の分解斜視図である。 [0023] 8 to 10 the number of balls rolling element and five, in and show a second embodiment which is adapted to tilt the ball rolling element by another tilting mechanism, Figure 8 is a longitudinal side view, FIG. 9 is the sectional view taken along line B-B, Fig. 10 is an exploded perspective view of the shifter and the swinging member.

【0024】この第2の実施例と第1の実施例の構造上の大きな相違点は、シフターと揺動部材の構造で、次のような構造となっている。 The significant difference in structure of the second embodiment and the first embodiment is the structure of the shifter and the swinging member, and has a following structure.

【0025】すなわち、シフター121の構造を図10 [0025] That is, the structure of shifter 121 10
に示すように、多条突条122を形成して断面をラック状としたものとし、揺動部材110は前記多条突条12 As shown in, and that the cross-section and the rack-shaped to form a multi-start projection 122, the swing member 110 is the multi-start ridges 12
2と噛合するセクタギヤ101を片側に設け、反対側にボール転動子8の外輪9を係合させる半月溝100を設けた構造としたものである。 Provided sector gear 101 to 2 engaged on one side, it is obtained by a structure in which a half-moon groove 100 to engage the outer ring 9 of the ball rolling element 8 on the other side.

【0026】この構造によると、第1の実施例と同様、 [0026] According to this structure, as in the first embodiment,
変速軸19を回動させて、ピニオン18,それと噛合する多条突条16を備えたシフトドラム17及びボールベアリング15を介してシフター121を原動軸2上を横動させることにより、シフター121の多条突条12 The transmission shaft 19 is rotated, the pinion 18 therewith by causing the shifter 121 via the shift drum 17 and the ball bearing 15 provided with a multi-start protrusions 16 meshing is horizontally moved on the driving shaft 2, the shifter 121 multi-threaded ridges 12
2,それと噛合するセキタギヤ101を介して揺動部材110を揺動するので、その半月溝100に外輪9を係合させた5個のボール転動子8,8、8,8,8は同時に揺動し、第1の実施例と同様、図11に示すように正転←→停止←→逆転の動作をさせることができる。 2, the same since the swing the swing member 110 through a Sekitagiya 101 in mesh, the half-moon groove 100 5 balls rolling element 8,8,8,8,8 that engaged the outer ring 9 at the same time swings, as in the first embodiment, it is possible to forward rotation ← → stop ← → operation of reverse rotation as shown in FIG. 11.

【0027】 [0027]

【発明の効果】本発明によれば正転←→停止←→逆転を行なわせることができるボール転動子を用いた無段変速装置を提供することができる。 According to the present invention in accordance Invite forward ← → Stop ← → it is possible to provide a continuously variable transmission using a ball rolling members that can perform reverse rotation. ボール転動子はボールベアリングの製造技術を利用できるので、精度の高い無段変速装置を製造することができる。 Since the ball rolling members are available fabrication techniques of the ball bearing, it is possible to manufacture a highly accurate stepless transmission. また、トルクカムによる圧接作用と共に遠心力による圧接作用が仂き、小型で動力伝達能力が大で、かつ動力伝達効率のよい無段変速装置を提供することができる。 Further, it is possible to press-contact action by the centrifugal force with pressure action by the torque cam is-out 仂, power transmission capacity large in size, and provides a continuously variable transmission with good power transfer efficiency.

【図面の簡単な説明】 BRIEF DESCRIPTION OF THE DRAWINGS

【図1】本発明の第1の実施例の縦断側面図である。 1 is a vertical sectional side view of a first embodiment of the present invention.

【図2】図1のA−A線断面図だある。 2 is s sectional view taken along line A-A of FIG.

【図3】本発明の第1の実施例の内部に組み込んだ部品の分解斜視図である。 3 is an exploded perspective view of the components incorporated within the first embodiment of the present invention.

【図4】本発明実施に用いることができる各種ボール転動子の構造例を示す図である。 It is a diagram showing a structural example of various ball rolling element which [4] can be used in the present invention embodiment.

【図5】微動ハンドル装置の動作説明展開図である。 Figure 5 is an operation explanatory development view of the fine control handle device.

【図6】本発明の第1の実施例の変速動作説明図である。 6 is a shift operation explanatory view of a first embodiment of the present invention.

【図7】ボール転動子と揺動部材の調心作用を説明する図である。 7 is a diagram illustrating an aligning action of the balls rolling members and the swinging member.

【図8】本発明の第2の実施例の縦断側面図である。 8 is a vertical sectional side view of a second embodiment of the present invention.

【図9】図8のB−B線断面図である。 9 is a sectional view taken along line B-B of FIG.

【図10】本発明の第2の実施例におけるシフターと揺動部材の分解斜視図である。 Is an exploded perspective view of the shifter and the swing member in the second embodiment of the present invention; FIG.

【図11】本発明の第2の実施例の変速動作説明図である。 11 is a shift operation explanatory diagram of a second embodiment of the present invention.

【符号の説明】 DESCRIPTION OF SYMBOLS

1 ケーシング 2 原動軸 3 従動軸 4 従動車 5 トルクカム 6 軌道リング 7 止ビス 8 ボール転動子 9 外輪 10 半月溝 11 揺動部材 12 シフター 13 凹部 14 原動キャリア 14a 爪片 15 ボールベアリング 16 多条突条 17 シフトドラム 18 ピニオン 19 変速軸 20 微動ハンドル装置 21 ハンドル 201 固定冠歯車 202 可撓性冠歯車 203 ボール 204 原動円板 1 casing 2 driving shaft 3 driven shaft 4 driven wheel 5 the torque cam 6 raceway ring 7 screwed 8 ball rolling members 9 the outer ring 10 half moon groove 11 swing member 12 shifter 13 recess 14 driving the carrier 14a pawl 15 ball bearing 16 Tajo突Article 17 shift drum 18 the pinion 19 gear shaft 20 fine control handle 21 handle 201 fixed crown gear 202 flexible crown gear 203 ball 204 driving disc

Claims (1)

    【特許請求の範囲】 [The claims]
  1. 【請求項1】 ケーシングの両側に、同一軸線上に配置した原動軸と従動軸を枢着し、この従動軸の端部にトルクカムを介して従動車を設けると共に、この従動車と対向させた軌道リングを前記ケーシングに固定し、この軌道リングと前記従動車間にそれぞれ球面上の一点において圧接係合する適数の外輪付ボール転動子を遊星状に配置し、これらボール転動子を一定間隔を保持し乍ら回動するフオーク状の原動キャリアを原動軸に設け、且つ前記ボール転動子の外輪に半月溝を係合させた揺動部材を介して全ボール転動子を同時に傾斜させるシフターを原動軸上に摺動自在に設けたことを特徴とする無段変速装置。 On both sides of 1. A casing, pivotally mounted the driving shaft and the driven shaft arranged on the same axis, provided with a driven wheel via a torque cam on the end of the driven shaft, was opposed to the driven wheel the orbital ring is fixed to the casing, the appropriate number of balls rolling element with an outer ring for pressing engagement arranged in planetary form at one point on each the track ring and to the driven vehicle spherical, certain of these ball rolling members provided fork-like driving carrier 乍Ra rotate holding the distance to the drive shaft, and the ball rolling elements of the outer ring to the half-moon groove via a swinging member which is engaged the whole ball rolling members simultaneously inclined continuously variable transmission, wherein a shifter which is provided slidably on the driving shaft.
JP27517596A 1996-09-11 1996-09-11 Continuously variable transmission Pending JPH1089435A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP27517596A JPH1089435A (en) 1996-09-11 1996-09-11 Continuously variable transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP27517596A JPH1089435A (en) 1996-09-11 1996-09-11 Continuously variable transmission

Publications (1)

Publication Number Publication Date
JPH1089435A true JPH1089435A (en) 1998-04-07

Family

ID=17551722

Family Applications (1)

Application Number Title Priority Date Filing Date
JP27517596A Pending JPH1089435A (en) 1996-09-11 1996-09-11 Continuously variable transmission

Country Status (1)

Country Link
JP (1) JPH1089435A (en)

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