JPS6333588B2 - - Google Patents
Info
- Publication number
- JPS6333588B2 JPS6333588B2 JP13956181A JP13956181A JPS6333588B2 JP S6333588 B2 JPS6333588 B2 JP S6333588B2 JP 13956181 A JP13956181 A JP 13956181A JP 13956181 A JP13956181 A JP 13956181A JP S6333588 B2 JPS6333588 B2 JP S6333588B2
- Authority
- JP
- Japan
- Prior art keywords
- face
- movable
- belt
- weight
- movable face
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000005540 biological transmission Effects 0.000 claims description 20
- 238000004804 winding Methods 0.000 claims description 7
- 230000000694 effects Effects 0.000 description 3
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/52—Pulleys or friction discs of adjustable construction
- F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmissions By Endless Flexible Members (AREA)
Description
【発明の詳細な説明】
本発明はベルト式自動変速機の改良に係り、特
に駆動側プーリの可動フエースの背面側にスプリ
ングを設け、該スプリングで可動フエースを固定
フエース側に常時押圧付勢することにより、ウエ
イトローラの遠心力負担を軽減せしめ、以つて装
置の可及的小型、軽量化、変速特性の改善等を図
るようにしたベルト式自動変速機に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement of a belt-type automatic transmission, and in particular, a spring is provided on the back side of the movable face of the driving pulley, and the spring constantly presses and biases the movable face toward the fixed face. This invention relates to a belt-type automatic transmission that reduces the centrifugal force burden on weight rollers, thereby making the device as compact and lightweight as possible, and improving speed change characteristics.
ベルト式自動変速機は、従来より種々の機械装
置に有用なる無段変速機として適用されている。
この種ベルト式自動変速機においては、駆動軸と
被動軸に配設されたプーリ間に張架されたベルト
の各々のプーリーに対する有効巻掛径を軸速度に
比例して発生する遠心力を利用して変更すること
により、変速が成されている。 Belt type automatic transmissions have conventionally been applied as continuously variable transmissions useful in various mechanical devices.
This type of belt-type automatic transmission uses centrifugal force generated in proportion to the shaft speed to change the effective winding diameter of the belt stretched between the pulleys arranged on the drive shaft and the driven shaft. Shifting is accomplished by changing the speed.
ところで、被動側プーリでのベルトのスリツプ
を防止するためには、可動フエースを或る程度強
い力で固定フエース側に押圧しておく必要があ
る。可動フエースの押圧力が増せば、ベルトのス
リツプは防止される反面、変速に必要な力、即ち
駆動側プーリの可動フエースを固定フエース側へ
移動せしめる押圧力が増大されねばならない。こ
の押圧力はウエイトローラに作用する遠心力に比
例し、遠心力はウエイトローラの重量に比例する
ため、上記押圧力を増大せしめるには、結局ウエ
イトローラの重量、サイズの増大を図らねばなら
ず、ためにプーリが大型化、高重量化する等の不
都合があつた。 By the way, in order to prevent the belt from slipping on the driven pulley, it is necessary to press the movable face toward the fixed face with a certain degree of strong force. If the pressing force of the movable face is increased, belt slip is prevented, but the force required for speed change, that is, the pressing force of the driving pulley to move the movable face toward the fixed face must be increased. This pressing force is proportional to the centrifugal force acting on the weight roller, and since centrifugal force is proportional to the weight of the weight roller, in order to increase the above pressing force, it is necessary to increase the weight and size of the weight roller. Therefore, there were disadvantages such as the pulley becoming larger and heavier.
本発明者は、この種のベルト式自動変速機の上
記不都合に鑑み、これを有効、且つ合理的に解消
すべく本発明を成したもので、その目的とする処
は、駆動軸に設けられた可動フエースの背面側
に、半径方向に移動可能なウエイトローラを回転
方向に均等に配設し、ベルトプーリに対するベル
トの有効巻掛径をウエイトローラに作用する遠心
力で以て変更させるベルト式自動変速機におい
て、可動フエースの背面側であつて、ウエイトロ
ーラの移動可能な範囲の径内に、複数のスプリン
グを回転方向に均等に配設し、このスプリングで
可動フエースを固定フエース側に常時押圧付勢す
ることによつて、ウエイトローラの遠心力負担を
軽減させて、ウエイトローラの小型、軽量化を図
り、また、可動フエースの大型化を防止し、以
て、装置全体の可及的小型化、軽量化、変速特性
の改善を図るとともに、可動フエースのたおれを
防止して、可動フエースと駆動軸との摺動性の向
上を図ることができるベルト式自動変速機を提供
するにある。 In view of the above-mentioned disadvantages of this type of belt type automatic transmission, the present inventor has created the present invention in order to effectively and rationally solve the problem. A belt type system in which radially movable weight rollers are arranged evenly in the rotational direction on the back side of the movable face, and the effective winding diameter of the belt around the belt pulley is changed by centrifugal force acting on the weight rollers. In an automatic transmission, a plurality of springs are arranged evenly in the rotational direction on the back side of the movable face within the movable range of the weight roller, and these springs always keep the movable face on the fixed face side. By pressing and energizing, the centrifugal force burden on the weight roller is reduced, making the weight roller smaller and lighter, and also preventing the movable face from increasing in size, thereby making the entire device as large as possible. To provide a belt type automatic transmission which is smaller in size, lighter in weight, has improved transmission characteristics, prevents the movable face from collapsing, and improves the slidability between the movable face and the drive shaft. .
以下に本発明の好適一実施例を添付図面に基づ
いて詳述する。 A preferred embodiment of the present invention will be described below in detail with reference to the accompanying drawings.
第１図は本発明に係る自動変速機の横断側面
図、第２図は第１図２―２線断面図である。 FIG. 1 is a cross-sectional side view of an automatic transmission according to the present invention, and FIG. 2 is a sectional view taken along line 2--2 in FIG.
第１図中１は駆動軸で、これの一方の延出端１
ａには可変プーリ２が配設されており、他端１ｂ
は例えば原動機（図示せず）の出力軸に連結され
ている。プーリ２は軸端に嵌着された皿状の固定
フエース３と、該固定フエース３と対面する如く
軸１上で軸方向に摺動自在に設けられた皿状の可
動フエース４とから成る。可動フエース４はスリ
ーブ７に、軸方向に摺動可能に取り付けられ、可
動フエース４の反固定フエース側の背面には複数
（図示例では６個）のウエイトローラ５…が第２
図に示す如く放射状に配設され、ウエイトローラ
５…は可動フエース４の背面とこれを塞ぐ如く設
けられたランププレート６間で保持されている。
ランププレート６は可動フエース４と軸方向に摺
動自在に係合して且つ軸１の回転を伝達する様に
軸方向はスリーブ７，８にて拘束されて定位置に
保持され、ローラ５…は可動フエース４の背面傾
斜ガイド部４ａとプレート６の対称的な傾斜ガイ
ド部部６ａ間に臨んでいる。 In Figure 1, 1 is the drive shaft, one of the extending ends 1
A variable pulley 2 is disposed at the other end 1b.
is connected, for example, to the output shaft of a prime mover (not shown). The pulley 2 consists of a plate-shaped fixed face 3 fitted to the shaft end, and a plate-shaped movable face 4 provided so as to be slidable in the axial direction on the shaft 1 so as to face the fixed face 3. The movable face 4 is attached to the sleeve 7 so as to be slidable in the axial direction, and a plurality of (six in the illustrated example) weight rollers 5 are mounted on the back surface of the movable face 4 on the side opposite to the fixed face.
As shown in the figure, the weight rollers 5 are arranged radially, and are held between the back surface of the movable face 4 and a ramp plate 6 provided so as to close this.
The lamp plate 6 is slidably engaged with the movable face 4 in the axial direction, and is restrained in the axial direction by sleeves 7 and 8 so as to transmit the rotation of the shaft 1, and held in a fixed position, and is held in a fixed position by the rollers 5... faces between the rear inclined guide portion 4a of the movable face 4 and the symmetrical inclined guide portion 6a of the plate 6.
又上記可動フエース４とランププレート６間
で、ウエイトローラ５の移動可能な範囲の径内で
かつウエイトローラ５…間に形成される空間部に
は、複数（図示例では３個）のスプリング９…が
回転方向に均等に縮装され、可動フエース４はこ
れらスプリング９…の弾発作用で常時固定フエー
ス３側、即ちプーリ２に巻掛けられたＶベルト１
０の巻掛径を拡大する方向へ押圧付勢されてい
る。即ち、各スプリング９は第１図に示す如く可
動フエース４の背面側に形成された円環状受け座
４ｂと、ランププレート６の前記座４ｂと対向す
る位置に形成された円形溝状の受け座６ｂ間にス
プリングガイド部４ｃにガイドされて装架されて
いる。尚可動フエース４の背面より一体的に突出
する上記円柱状のスプリングガイド部４ｃはラン
ププレート６側の受け座６ｂ内まで臨んでその先
部が受け座６ｂにオーバーラツプしているため、
スプリング９が抜け落ちることはない。 In addition, a plurality of (three in the illustrated example) springs 9 are provided in a space formed between the movable face 4 and the ramp plate 6, within the movable range of the weight roller 5, and between the weight rollers 5. ... are compressed evenly in the rotational direction, and the movable face 4 is used for the spring force of these springs 9..., and the V-belt 1 is always fixed on the side of the fixed face 3, that is, the V-belt 1 is wound around the pulley 2.
It is pressed and biased in the direction of enlarging the winding diameter of 0. That is, each spring 9 has an annular receiving seat 4b formed on the back side of the movable face 4 and a circular groove-shaped receiving seat formed on the lamp plate 6 at a position facing the seat 4b, as shown in FIG. 6b, and is guided by a spring guide portion 4c and mounted thereon. The cylindrical spring guide portion 4c integrally protruding from the back surface of the movable face 4 extends into the receiving seat 6b on the lamp plate 6 side, and its tip overlaps with the receiving seat 6b.
The spring 9 will not fall out.
一方、被動軸１１は前記駆動軸１と平行に設け
られ、被動軸１１の延出端部１１ａには発進クラ
ツチ１２が設けられている。即ち、被動軸１１の
軸端にはドラム状のクラツチアウタ１３が設けら
れ、アウタ１３にはドラム部１３ａ内壁に接する
摩擦係合部材であるクラツチシユー１４が対向す
る如く設けられている。一方、被動軸１１の外側
には軸受１５，１５を介して固定フエースボス１
６が嵌装され、ボス１６端部には駆動プレート１
７が固設され、プレート１７には上記クラツチシ
ユー１４に対応する遠心拡開素子１８が設けられ
ている。尚１９はクラツチダンパーラバーであ
る。 On the other hand, a driven shaft 11 is provided parallel to the drive shaft 1, and a starting clutch 12 is provided at an extending end 11a of the driven shaft 11. That is, a drum-shaped clutch outer 13 is provided at the shaft end of the driven shaft 11, and a clutch shoe 14, which is a frictional engagement member that contacts the inner wall of the drum portion 13a, is provided on the outer 13 so as to face it. On the other hand, a fixed face boss 1 is provided on the outside of the driven shaft 11 via bearings 15, 15.
6 is fitted, and the drive plate 1 is fitted to the end of the boss 16.
7 is fixedly attached, and the plate 17 is provided with a centrifugal expansion element 18 corresponding to the clutch 14 described above. Note that 19 is a clutch damper rubber.
上記固定フエースボス１６の他端部には可変プ
ーリ２０の皿状固定フエース２１が固設され、こ
の固定フエース２１に対向する可動フエース２２
は固定フエースボス１６の外周に軸方向に摺動自
在、且つ周方向に回転可能に嵌合された可動フエ
ースボス２３の端部に固着されており、該可動フ
エース２２の内側内端部と固定フエースボス１６
側の駆動プレート１７間にはスプリング２４が縮
装され、該スプリング２４により可動フエース２
２は固定フエース２１側へ、即ちプーリ径を拡大
する側へ弾圧されている。そして可動フエースボ
ス２３の円周複数箇所にはガイドピン２５…が下
方へ突設され、各ガイドピン２５の下部に回動自
在に嵌装されたガイドローラ２６は固定フエース
ボス１６に形成された軸方向に長孔で周方向に傾
斜したカム溝１６ａに係合しており、このガイド
ピン２５のガイドローラ２６を介してのカム溝１
６ａとの係合で可動フエースボス２３及びこれに
固設された可動フエース２２は軸方向の移動が可
能となる。而して駆動側プーリ２と被動側プーリ
２０間にはＶベルト１０が張架されている。 A dish-shaped fixed face 21 of a variable pulley 20 is fixed to the other end of the fixed face boss 16, and a movable face 22 facing the fixed face 21
is fixed to the end of a movable face boss 23 fitted to the outer circumference of the fixed face boss 16 so as to be slidable in the axial direction and rotatable in the circumferential direction, and the inner end of the movable face 22 and the fixed face boss 16
A spring 24 is compressed between the side drive plates 17, and the spring 24 moves the movable face 2.
2 is pressed toward the fixed face 21 side, that is, toward the side that enlarges the pulley diameter. Guide pins 25 are provided at multiple locations on the circumference of the movable face boss 23 to protrude downward, and a guide roller 26 rotatably fitted in the lower part of each guide pin 25 is moved in the axial direction formed on the fixed face boss 16. The cam groove 16a of the guide pin 25 is engaged with the cam groove 16a inclined in the circumferential direction through a long hole in the cam groove 16a.
6a allows the movable face boss 23 and the movable face 22 fixed thereto to move in the axial direction. A V-belt 10 is stretched between the driving pulley 2 and the driven pulley 20.
次に本変速機の作用及び効果について述べる。 Next, the functions and effects of this transmission will be described.
第１図は駆動軸１が低速回転している状態を示
し、不図示の原動機等からの動力は駆動軸１、駆
動側プーリ２、Ｖベルト１０、被動側プーリ２０
へと伝達され、被動側プーリ２０が回転せしめら
れる。この被動側プーリ２０と一体に固定フエー
スボス１６及び可動フエースボス２３が回転し、
更に駆動プレート１７は固定フエースボス１６と
ともに回転し、これ１７に設けられた遠心拡開子
１８は遠心力で拡開され、これに固着したクラツ
チシユー１４をクラツチアウタ１３のドラム部１
３ａに押圧し、クラツチアウタ１３を介して被動
軸１１を回転せしめる。この場合は前述の如く駆
動軸１の回転速度が低いため、ウエイトローラ５
…に作用する遠心力はＶベルト１０のプーリ２に
対する巻掛径を拡大せしめるには至らず、従つ
て、第１図に示す如く駆動側プーリ２の巻掛径は
小さく、被動側プーリ２０のそれは大きく保持さ
れ、被動軸１１の回転は減速され、又これの回転
トルクは増幅される。 FIG. 1 shows a state in which the drive shaft 1 is rotating at a low speed, and power from a prime mover (not shown) is transmitted to the drive shaft 1, the drive pulley 2, the V-belt 10, and the driven pulley 20.
The driven pulley 20 is rotated. The fixed face boss 16 and the movable face boss 23 rotate together with this driven pulley 20,
Further, the drive plate 17 rotates together with the fixed face boss 16, and the centrifugal expander 18 provided on this 17 is expanded by centrifugal force, and the clutch shoe 14 fixed thereto is moved to the drum portion 1 of the clutch outer 13.
3a to rotate the driven shaft 11 via the clutch outer 13. In this case, since the rotational speed of the drive shaft 1 is low as described above, the weight roller 5
The centrifugal force acting on... does not increase the winding diameter of the V-belt 10 around the pulley 2. Therefore, as shown in FIG. It is held large, the rotation of the driven shaft 11 is slowed down, and its rotational torque is amplified.
駆動軸１の回転速度が上昇すれば、ウエイトロ
ーラ５…はこれらに作用する遠心力によつて半径
方向外方へ放射状に移動し、可動フエース４を固
定フエース３側へ押圧する。この場合可動フエー
ス４にはスプリング９…の作用により常時これ４
を固定フエース３側へ押圧する力が作用している
ため、結局可動フエース４にはスプリング９…に
よる押圧力と前記ウエイトローラ５…の移動によ
つて発生する押圧力の合力が作用し、従つて、従
来のウエイトローラによつてのみ押圧力を発生せ
しめるものに比し、ウエイトローラ５…の遠心力
負担をスプリング９…の弾発力分だけ軽減するこ
とができる。遠心力の大きさはウエイトローラの
重量に比例する故、ウエイトローラ５…の遠心力
の負担軽減は、これらウエイトローラ５…が小
型、軽量化されることを、更には装置全体が小
型、コンパクト化されることを意味している。 When the rotational speed of the drive shaft 1 increases, the weight rollers 5 move radially outward due to the centrifugal force acting on them, and press the movable face 4 toward the fixed face 3. In this case, the movable face 4 is always supported by the action of the spring 9.
Since a force is acting to press the fixed face 3 toward the fixed face 3, the resultant force of the pressing force generated by the springs 9 and the pressing force generated by the movement of the weight rollers 5 acts on the movable face 4, and Therefore, compared to the conventional weight rollers that generate pressing force only, the centrifugal force burden on the weight rollers 5 can be reduced by the elastic force of the springs 9. Since the magnitude of centrifugal force is proportional to the weight of the weight rollers, reducing the burden of centrifugal force on the weight rollers 5 means that these weight rollers 5 can be made smaller and lighter, and the entire device can be made smaller and more compact. It means to be transformed.
ところで、可動フエース４に上記合力が作用す
る結果、固定フエース３と可動フエース４間の間
隔は狭められ、プーリ２のベルト巻掛径は拡大す
る。一方、ベルト１０の駆動側プーリ２による拡
径引張動により被動側プーリ２０にあつては、該
ベルト１０は固定フエース２１と可動フエース２
２間の半径方向内方へ喰い込む。これに伴つて可
動フエース２２はスプリング２４の弾発力に抗し
て図中左動し、ベルト１０のプーリ２０への巻掛
径は緒小し、被動軸１１の回転は増速される。 By the way, as a result of the resultant force acting on the movable face 4, the distance between the fixed face 3 and the movable face 4 is narrowed, and the belt winding diameter of the pulley 2 is increased. On the other hand, when the driven pulley 20 is pulled by the driving pulley 2 to expand the diameter of the belt 10, the belt 10 is moved between the fixed face 21 and the movable face 2.
Cut inward in the radial direction between the two. Along with this, the movable face 22 moves to the left in the figure against the elastic force of the spring 24, the winding diameter of the belt 10 around the pulley 20 becomes smaller, and the rotation speed of the driven shaft 11 is increased.
次に本発明の要旨たるスプリング９…を付加し
たことの効果を第３図に基づいて考察する。 Next, the effect of adding the springs 9, which is the gist of the present invention, will be discussed based on FIG.
第３図は可動フエース４に作用する押圧力Ｆと
回転速度Ｎとの関係（押圧力特性）を示すグラフ
であり、縦軸は押圧力Ｆ、横軸は回転速度Ｎであ
る。 FIG. 3 is a graph showing the relationship (pressing force characteristics) between the pressing force F acting on the movable face 4 and the rotational speed N, where the vertical axis is the pressing force F and the horizontal axis is the rotational speed N.
第３図中破線で示す曲線Ａは従来の変速機の押
圧力特性を示し、この時の押圧力はウエイトロー
ラに作用する遠心力に比例し、又遠心力は回転速
度Ｎの２乗に比例する故、これＡは原点Ｏを通る
二次曲線となる。 Curve A shown by the broken line in Fig. 3 shows the pressing force characteristics of the conventional transmission.The pressing force at this time is proportional to the centrifugal force acting on the weight roller, and the centrifugal force is proportional to the square of the rotational speed N. Therefore, this A becomes a quadratic curve passing through the origin O.
又同図中鎖線にて示す曲線Ｂは同じく従来の変
速機の押圧力特性を示すが、この時のウエイトロ
ーラ重量は曲線Ａのものより大きく、従つてこの
曲線Ｂの勾配は曲線Ａのそれよりも大きく、同一
速度ならばより大きな押圧力が発生する。 Curve B shown by the dashed line in the figure also shows the pressing force characteristics of the conventional transmission, but the weight roller weight at this time is greater than that of curve A, so the slope of curve B is similar to that of curve A. If the speed is the same, a larger pressing force will be generated.
今、変速せしめるに要する押圧力をF1とすれ
ば、特性Ｂの変速機にあつては回転速度N1で変
速するのに対し、特性Ａのウエイトローラ重量の
小さい変速機にあつては回転速度をN2まで上昇
させねば変速を開始しない。見方を換えれば、特
性Ａの変速機にあつて回転速度N1にて変速する
には、そのウエイトローラ重量を大きくしてその
押圧力特性を曲線Ｂに示すような特性に変更せね
ばならない。 Now, if the pressing force required to shift is F 1 , a transmission with characteristic B will shift at a rotational speed of N 1 , whereas a transmission with characteristic A, where the weight roller is small, will rotate at a rotational speed of N 1. It will not start shifting unless the speed increases to N2 . Looking at it from another perspective, in order to shift at a rotational speed N1 in a transmission with characteristic A, the weight roller must be increased in weight and its pressing force characteristics must be changed to those shown by curve B.
ところが、本発明に係る変速機にあつては、可
動フエース４には常時F0なる一定の押圧力（第
３図中直線Ｃにて示される。）が作用しているた
め、ウエイトローラ重量が前記特性Ａのそれと同
等で小さい場合においてさえ、その押圧力特性は
曲線Ｄ、即ち曲線Ａを縦軸上方へF0だけ平行移
動させた曲線になり、第３図より明らかな如く回
転速度N1にて変速することができる。 However, in the transmission according to the present invention, since a constant pressing force F0 (indicated by straight line C in FIG. 3) is always acting on the movable face 4, the weight roller weight is Even in the case where the pressure force is equal to and smaller than that of the characteristic A, the pressing force characteristic becomes a curve D, that is, a curve obtained by translating the curve A upward by F 0 on the vertical axis, and as is clear from FIG. 3, the rotation speed N 1 You can change gears with.
斯くして、可動フエースの背面側に配設された
ウエイトローラの移動可能な範囲の径内に、複数
のスプリングを回転方向に均等に配設し、このス
プリングで可動フエースを固定フエース側に常時
押圧付勢することによつて、スプリングに押圧力
を負担せしめ、その分ウエイトローラの押圧力の
負担を軽減せしめることにより、ウエイトローラ
の小型、軽量化を図り、また、スプリングとウエ
イトローラを回転方向に配設することにより、可
動フエースの径方向の大型化を防止し、以て、装
置全体の小型、軽量化を図るとともに、可動フエ
ースのたおれを防止して、可動フエースと駆動軸
との摺動性の向上を図ることができる。 In this way, a plurality of springs are arranged evenly in the rotational direction within the movable range of the weight roller arranged on the back side of the movable face, and these springs always keep the movable face on the fixed face side. By energizing the spring, the pressure is applied to the spring, which reduces the burden of the pressure on the weight roller, which makes the weight roller smaller and lighter, and also allows the spring and weight roller to rotate. By arranging the movable face in the radial direction, it is possible to prevent the movable face from increasing in size in the radial direction, thereby reducing the size and weight of the entire device. It is possible to improve sliding properties.
又上記スプリングのバネ定数を適当に選定する
ことにより、ウエイトローラの重量、サイズを変
更することなく所要の押圧力特性、即ち変速特性
が容易に得られる。 Furthermore, by appropriately selecting the spring constant of the spring, the required pressing force characteristics, ie, speed change characteristics, can be easily obtained without changing the weight or size of the weight roller.
本発明によれば、以上の如き多大の効果を奏す
ることができる。 According to the present invention, the above-mentioned great effects can be achieved.
図面は本発明の一実施例を示し、第１図は本発
明に係る自動変速機の横断側面図、第２図は第１
図２―２線断面図、第３図は可動フエースに作用
する押圧力と回転速度との関係を示すグラフであ
る。
尚図面中１は駆動軸、２は駆動側プーリ、３，
２１は固定フエース、４，２２は可動フエース、
５はウエイトローラ、９，２４はスプリング、１
０はＶベルト、１１は被動軸、１６は固定フエー
スボス、２０は被動側プーリ、２３は可動フエー
スボスである。
The drawings show one embodiment of the present invention, FIG. 1 is a cross-sectional side view of an automatic transmission according to the present invention, and FIG.
2-2 line sectional view and FIG. 3 are graphs showing the relationship between the pressing force acting on the movable face and the rotational speed. In the drawing, 1 is the drive shaft, 2 is the drive pulley, 3,
21 is a fixed face, 4 and 22 are movable faces,
5 is a weight roller, 9, 24 is a spring, 1
0 is a V-belt, 11 is a driven shaft, 16 is a fixed face boss, 20 is a driven pulley, and 23 is a movable face boss.
Claims (1)
スとから構成されるベルトプーリを夫々配設し、
前記駆動軸に設けられた可動フエースの背面側
に、半径方向に移動可能なウエイトローラを回転
方向に均等に配設し、前記両ベルトプーリ間に張
架されたベルトの前記各々のベルトプーリに対す
る有効巻掛径を前記ウエイトローラに作用する遠
心力で以つて変更させるようにしたベルト式自動
変速機において、 前記駆動軸に設けられた可動フエースの背面側
であつて、前記ウエイトローラの移動可能な範囲
の径内に、前記可動フエースを固定フエース側に
押圧付勢する複数のスプリングを回転方向に均等
に配設したことを特徴とするベルト式自動変速
機。[Claims] 1. Belt pulleys each consisting of a fixed face and a movable face are arranged on the driving shaft and the driven shaft,
Weight rollers movable in the radial direction are arranged evenly in the rotational direction on the back side of the movable face provided on the drive shaft, and weight rollers that are movable in the radial direction are arranged evenly in the rotational direction, so that the belt stretched between the two belt pulleys can In a belt-type automatic transmission in which the effective winding diameter is changed by centrifugal force acting on the weight roller, a movable portion of the weight roller is located on the back side of the movable face provided on the drive shaft. 1. A belt-type automatic transmission characterized in that a plurality of springs for pressing and biasing the movable face toward the fixed face are arranged evenly in the rotational direction within a diameter range.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13956181A JPS5839868A (en) | 1981-09-04 | 1981-09-04 | Belt type automatic speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13956181A JPS5839868A (en) | 1981-09-04 | 1981-09-04 | Belt type automatic speed change gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5839868A JPS5839868A (en) | 1983-03-08 |
| JPS6333588B2 true JPS6333588B2 (en) | 1988-07-06 |
Family
ID=15248126
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13956181A Granted JPS5839868A (en) | 1981-09-04 | 1981-09-04 | Belt type automatic speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5839868A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006046324A (en) * | 2004-07-08 | 2006-02-16 | Yamaha Motor Co Ltd | Power unit |
| CN100355622C (en) * | 2004-07-08 | 2007-12-19 | 雅马哈发动机株式会社 | Power unit |
| EP2048411A1 (en) | 2004-07-02 | 2009-04-15 | Yamaha Hatsudoki Kabushiki Kaisha | V-belt continuously variable transmission for small vehicle and straddle-type vehicle |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0680341B2 (en) * | 1984-12-28 | 1994-10-12 | ヤマハ発動機株式会社 | V-belt type automatic transmission |
| JPS61165058A (en) * | 1985-01-16 | 1986-07-25 | Yamaha Motor Co Ltd | Manufacture of weight for v-belt type automatic transmission |
| JPH0689823B2 (en) * | 1985-02-01 | 1994-11-14 | ヤマハ発動機株式会社 | V-belt type automatic transmission |
| JPH0684775B2 (en) * | 1985-02-01 | 1994-10-26 | ヤマハ発動機株式会社 | V-belt type automatic transmission |
| JPH02180342A (en) * | 1988-12-29 | 1990-07-13 | Bando Chem Ind Ltd | Belt type continuous transmission with centrifugal weight |
| CA2052356C (en) * | 1991-09-27 | 1998-06-02 | Jean Robert | Driving pulley for a variable speed belt gear with tooth counter-weights |
-
1981
- 1981-09-04 JP JP13956181A patent/JPS5839868A/en active Granted
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2048411A1 (en) | 2004-07-02 | 2009-04-15 | Yamaha Hatsudoki Kabushiki Kaisha | V-belt continuously variable transmission for small vehicle and straddle-type vehicle |
| JP2006046324A (en) * | 2004-07-08 | 2006-02-16 | Yamaha Motor Co Ltd | Power unit |
| CN100355622C (en) * | 2004-07-08 | 2007-12-19 | 雅马哈发动机株式会社 | Power unit |
| JP4660286B2 (en) * | 2004-07-08 | 2011-03-30 | ヤマハ発動機株式会社 | Power unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5839868A (en) | 1983-03-08 |
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