JPS591861A - Mechanical stepless transmission gear - Google Patents
Mechanical stepless transmission gearInfo
- Publication number
- JPS591861A JPS591861A JP10969882A JP10969882A JPS591861A JP S591861 A JPS591861 A JP S591861A JP 10969882 A JP10969882 A JP 10969882A JP 10969882 A JP10969882 A JP 10969882A JP S591861 A JPS591861 A JP S591861A
- Authority
- JP
- Japan
- Prior art keywords
- cones
- fixed ring
- ring
- output shaft
- cone
- 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
Links
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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H37/0853—CVT using friction between rotary members having a first member of uniform effective diameter cooperating with different parts of a second member
-
- 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
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/16—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface
- F16H15/18—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface externally
- F16H15/20—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface externally co-operating with the outer rim of the member A, which is perpendicular or nearly perpendicular to the friction surface of the member B
Abstract
Description
【発明の詳細な説明】
本発明は、摩擦伝動装置を用いた機械式無段変速機に関
するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a mechanical continuously variable transmission using a friction transmission.
第１図は従来の摩擦伝動装置を用いた機械式無段変速機
を示すもので、回転数Ｎｉで回転する人力軸ａは１個の
コーンｂ、２個のリングＣ１゜Ｃ３、ギヤｄｘｌａ２を
介して出力軸ｅを回転数ＮＯで回転させる構成となって
いるが、このとき、入力軸ａの回転を逆転しなければ出
力軸ｅの回転方向を逆転することができなかった。さら
に、速度比Ｎｏ ／ Ｎ＋を小さくして高トルクを得る
ためには、コーンｂの先端部にリングＣ１，Ｃ２を移動
させなければならず、そのためコーンｂとリング（４、
Ｃ２の接触面積が減少し、コーンｂとリングｃｌ 、
Ｃ２の耐久性が悪くなるという欠点があった。Figure 1 shows a mechanical continuously variable transmission using a conventional friction transmission device.A human power shaft a rotating at a rotation speed Ni has one cone B, two rings C1°C3, and a gear dxla2. Although the configuration is such that the output shaft e is rotated at a rotational speed NO through the input shaft e, the direction of rotation of the output shaft e cannot be reversed unless the rotation of the input shaft a is reversed. Furthermore, in order to reduce the speed ratio No/N+ and obtain high torque, it is necessary to move rings C1 and C2 to the tip of cone b, so cone b and rings (4,
The contact area of C2 decreases, cone b and ring cl,
There was a drawback that the durability of C2 deteriorated.
本発明は上記のことにかんがみなされたもので、入力軸
の回転方向に関係なく出力軸の回転方向を逆転可能にし
、またコーンとリングとの接触面積を速度比に関係な（
一定に保つことができ、コーンとリングの耐久性を映″
上することができる機械式無段変速機を提供しようとす
るものである。The present invention has been made in consideration of the above-mentioned problems, and it is possible to reverse the rotational direction of the output shaft regardless of the rotational direction of the input shaft, and to change the contact area between the cone and the ring so that the rotational direction is independent of the speed ratio.
It can be kept constant and reflects the durability of the cone and ring.
The purpose of the present invention is to provide a mechanical continuously variable transmission that can increase the
以下本発明の実施例を第２図に基づいて説明する。Embodiments of the present invention will be described below with reference to FIG.
図中１は入力軸で、この入力軸１に２個のコーン２，３
が、それぞれの軸心を平行にし、かつ人力軸１に対して
傾斜させて回転自在に支持しである。上記両コーン２，
３は向きをそれぞれ反対にしてあり、両コーン２，３相
互の外側辺は入力軸１の軸心に対して同一距離で平行と
なるようにしである。４は両コーン２，３の外側辺に外
接する固定リングであり、この固定リング４は図示しな
い作動機構により入力軸Ｉの軸心方向に移動可能に、か
つ回転しないように支持しである。上記各コーン２，３
の支軸５゜６にはピニオン７．８が固着してあり、この
各ピニオン７．８は入力軸１と同一軸心上に配設した大
小のリングギヤ９，１０に噛合しである。In the figure, 1 is an input shaft, and two cones 2 and 3 are attached to this input shaft 1.
are supported rotatably with their axes parallel to each other and inclined with respect to the human-powered shaft 1. Both cones 2 above,
The cones 3 have opposite directions, and the outer sides of the cones 2 and 3 are parallel to each other at the same distance from the axis of the input shaft 1. Reference numeral 4 denotes a fixing ring that circumscribes the outer sides of both cones 2 and 3, and this fixing ring 4 is supported so as to be movable in the axial direction of the input shaft I and not rotated by an operating mechanism (not shown). Each of the above cones 2 and 3
Pinions 7.8 are fixed to the support shaft 5.6, and each pinion 7.8 meshes with large and small ring gears 9, 10 disposed coaxially with the input shaft 1.
そしてこの両リングギヤ９，１０は遊星機構１１を介し
て出力軸１２に連結しである。Both ring gears 9 and 10 are connected to an output shaft 12 via a planetary mechanism 11.
上記構成において、入力軸ｌが回転することにより、コ
ーン２，３の支軸５，６は入力軸１の軸心を中心として
公転する。両支軸５，６の公転により両コーン２，３は
固定リング４に接触して各支軸５，６と一体に自転する
。これにより各リングギヤ９，１０が固転され、これの
回転が遊星歯車１１を介して出力軸１２に伝達される。In the above configuration, as the input shaft 1 rotates, the support shafts 5 and 6 of the cones 2 and 3 revolve around the axis of the input shaft 1. Due to the revolution of both support shafts 5 and 6, both cones 2 and 3 come into contact with fixing ring 4 and rotate together with each support shaft 5 and 6. As a result, each of the ring gears 9 and 10 is fixedly rotated, and the rotation thereof is transmitted to the output shaft 12 via the planetary gear 11.
入力軸１から出力軸１２への回転伝達の変速は以下のよ
うになされる。The speed change of rotation transmission from the input shaft 1 to the output shaft 12 is performed as follows.
人力軸１の回転数をＮｉ、出力軸１２０回転数をＮｏ、
一方のコーン２の回転数をＮ２、他方のコーン３の回転
数をＮ３、一方のコーン２側のピニオン７の歯数をＺフ
、他方のピニオン８の歯数をＺＢ、一方のピニオン７に
噛合する大径のリングギヤ９の歯数を為、小径のリング
ギヤ１０の歯数をＺＩＯ，遊星歯車機構の太陽歯車の歯
数なＺｓ。The rotation speed of the human power shaft 1 is Ni, the output shaft 120 rotation speed is No.
The number of rotations of one cone 2 is N2, the number of rotations of the other cone 3 is N3, the number of teeth on the pinion 7 on one cone 2 side is ZF, the number of teeth on the other pinion 8 is ZB, and the number of teeth on one pinion 7 is The number of teeth of the large-diameter ring gear 9 to be engaged is ZIO, the number of teeth of the small-diameter ring gear 10 is ZIO, and the number of teeth of the sun gear of the planetary gear mechanism is Zs.
リングギヤの歯数をＺＲｌさらに両コーン２，３と固定
リング４との接触点から入力軸１の軸心までのそれぞれ
の距離をＲω、Ｒω、また各コーン２，３と固定リング
４との接触点からそれぞレノコーン２，３の軸心までの
距離をＲβ１．梗２とする。またプラスを正転、マイナ
スを逆転とする。なお正転は入力軸１がら見て右回転と
する。The number of teeth of the ring gear is ZRl, and the respective distances from the point of contact between both cones 2 and 3 and the fixed ring 4 to the axis of the input shaft 1 are Rω and Rω, and the contact between each cone 2 and 3 and the fixed ring 4 is The distances from the points to the axes of Renocones 2 and 3 are Rβ1. Let's call it 2nd stage. Plus means forward rotation, and minus means reverse rotation. Note that normal rotation is defined as clockwise rotation when viewed from the input shaft 1.
一方のコーン２の回転数Ｎ２は、
Ｒω
Ｎ２＝ Ｎｉ （１−、、−）・・印・・・・ （１）
他方のコーン３の回転数Ｎ３は、
大径のリングギヤ９の回転数Ｎ９は、
小径のリングギヤ１０の回転数ＮＩＯは、出力軸１２の
回転数Ｎｏは、
式（１）と（５）より、
・・・・・・・・・ （６）
式（６）において、Ｒβ１とｌψ２は固定リング４をコ
ーン２，３に沿って動かすことにより変化する。The rotation speed N2 of one cone 2 is Rω N2= Ni (1-,,-)...mark... (1)
The rotation speed N3 of the other cone 3 is: The rotation speed N9 of the large diameter ring gear 9 is: The rotation speed NIO of the small diameter ring gear 10 is: The rotation speed No of the output shaft 12 is: From equations (1) and (5), (6) In equation (6), Rβ1 and lψ2 are changed by moving the fixed ring 4 along the cones 2 and 3.
さらに２個のコーン２，３は図に示すように、向きを反
対にしてあり、また両コーン２，３の固定リング４に対
する機付学的位置関係は、固定リング４の移動により軸
方向左右に対称となる。このことは、各歯車における各
遊星機構１１により、入力回転方向と関係なく、出力軸
１２が逆転可能である。Further, as shown in the figure, the two cones 2 and 3 are oriented in opposite directions, and the mechanical positional relationship of both cones 2 and 3 with respect to the fixing ring 4 is changed by the movement of the fixing ring 4. It is symmetrical to This means that the output shaft 12 can be reversed by each planetary mechanism 11 in each gear, regardless of the input rotation direction.
例えば、Ｚ７＝２４、Ｚｑ ＝ ６５、ＺＢ ＝ ６５
、 Ｚｓ＝２０、ム＝３０、ＺＩＯ＝ ６０、ＲＡｌ
＝２．５Ｒβ１１Ｒβ１＝Ｒβ２とすると、速度比Ｎｏ
／Ｎｉはゼロになり、出力軸１２は停止する。For example, Z7=24, Zq=65, ZB=65
, Zs=20, Mu=30, ZIO=60, RAl
=2.5Rβ11Rβ1=Rβ2, speed ratio No.
/Ni becomes zero, and the output shaft 12 stops.
固定リング４を移動させて、Ｒβ１峙几β２の状態にす
ると、速度比Ｎｏ／Ｎｉは正または負の値をとり、出力
軸１２０回転方向も正または負となる。また固定リング
４が一方のコーン２の小径部に接触している場合は、他
方のコーン３においてはその大径部と接触しているため
、固定リング４と両コーン２，３との接触面積の総和は
、固定リング４の位置、すなわち、速度比Ｎｏ／Ｎｉに
よらず一定に保たれる。When the fixed ring 4 is moved to a state where Rβ1 is opposite to β2, the speed ratio No/Ni takes a positive or negative value, and the rotation direction of the output shaft 120 also becomes positive or negative. In addition, when the fixing ring 4 is in contact with the small diameter part of one cone 2, it is in contact with the large diameter part of the other cone 3, so the contact area between the fixing ring 4 and both cones 2 and 3 is The total sum is kept constant regardless of the position of the fixed ring 4, that is, the speed ratio No/Ni.
本発明に係る機械式無段変速機は、上記詳述したように
なり、２個のコーン２，３を、互いに向きを逆にし、か
つ相互の軸心を平行にする −と共に、両軸心を人力
軸１に対して傾斜させ、さらに両コーン２，３の外側辺
と入力軸１の軸心との距離Ｒωを等しくかつ平行になる
ようにして入力軸１に回転自在に支持し、この両コーン
２．３に外接する固定リング４を人力軸１の軸方向に移
動可能に設け、両コーン２，３の支軸５．６にビニオン
７．８を設け、この両ビニオン７．８に、入力軸ｌと同
一軸心上に支持したリングギヤ９，１０を噛合し、両リ
ングギヤｑ。The mechanical continuously variable transmission according to the present invention is as described in detail above, and has two cones 2 and 3 whose directions are opposite to each other and whose axes are parallel to each other. is tilted with respect to the human power axis 1, and is rotatably supported on the input shaft 1 so that the distances Rω between the outer sides of both cones 2 and 3 and the axis of the input shaft 1 are equal and parallel. A fixing ring 4 circumscribing both cones 2.3 is provided so as to be movable in the axial direction of the human power shaft 1, a pinion 7.8 is provided on the support shaft 5.6 of both cones 2 and 3, and a pinion 7.8 is provided on the support shaft 5.6 of both cones 2, 3. , ring gears 9 and 10 supported on the same axis as the input shaft l mesh with each other, and both ring gears q.
１０を遊星歯車機構１１を介して出力軸１２に連結した
から、固定リング４を移動することにより、入力軸１の
回転が出力軸１２に無段階に変速されて出力される。そ
して本発明によれば、固定リング４を移動することによ
り、入力軸の回転方向に関係なく出力軸の回転方向を逆
転することができ、さらに、速度比に関係な（コーン２
，３と固定リング４の接触面積を一定にすることができ
、コーン２，３と固定リング４の耐久性を向上すること
ができる。Since the input shaft 10 is connected to the output shaft 12 via the planetary gear mechanism 11, by moving the fixing ring 4, the rotation of the input shaft 1 is outputted to the output shaft 12 in a stepless manner. According to the present invention, by moving the fixed ring 4, the rotation direction of the output shaft can be reversed regardless of the rotation direction of the input shaft.
, 3 and the fixing ring 4 can be made constant, and the durability of the cones 2, 3 and the fixing ring 4 can be improved.
第１図は従来例を示す構成説明図、第２図は本発明の実
施例を示す構成説明図である。
１は入力軸、２，３はコーン、４は固定リング、５，６
は支軸、７，８はピニオン、９，１０はリングギヤ、１
１は遊星歯車、＋２は出力軸。
出願人 株式会社 小松製作所
代理人 弁理士 米 原 正 章
弁理士 浜 本 忠FIG. 1 is a configuration explanatory diagram showing a conventional example, and FIG. 2 is a configuration explanatory diagram showing an embodiment of the present invention. 1 is the input shaft, 2 and 3 are the cones, 4 is the fixing ring, 5 and 6
is the support shaft, 7 and 8 are pinions, 9 and 10 are ring gears, 1
1 is the planetary gear, +2 is the output shaft. Applicant Komatsu Ltd. Representative Patent Attorney Masaaki Yonehara Patent Attorney Tadashi Hamamoto
Claims (1)
の軸心を平行にすると共に１両軸心を人力軸１に対して
傾斜させ、さらに両コーン２゜３の外側辺と入力軸１の
軸心との距離几ωを等しくかつ平行になるようにして入
力軸１に回転自在九支持し、この両コーン２，３に外接
する固定リング４を入力軸１の軸方向に移動可能に設け
、両コーン２，３の支軸５，６にビニオン７゜８を設置
、この両ピニオン７．８に、入力軸Ｉと同一軸心上に支
持したリングギヤ９，１０を噛合し、両リングギヤ９，
１０を遊星歯車機構１１を介して出力軸１２に連結した
ことを特徴とする機械式無段変速機。The two cones 2 and 3 are turned in opposite directions, their axes are parallel to each other, and one axis is tilted to the human power axis 1, and the outer sides of both cones 2 and 3 are input. It is rotatably supported on the input shaft 1 so that the distance ω from the axis of the shaft 1 is equal and parallel, and the fixing ring 4 circumscribing both cones 2 and 3 is moved in the axial direction of the input shaft 1. A pinion 7.8 is installed on the support shafts 5, 6 of both cones 2, 3, and ring gears 9, 10 supported on the same axis as the input shaft I are meshed with both pinions 7.8. Both ring gears 9,
10 is connected to an output shaft 12 via a planetary gear mechanism 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10969882A JPS591861A (en) | 1982-06-28 | 1982-06-28 | Mechanical stepless transmission gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10969882A JPS591861A (en) | 1982-06-28 | 1982-06-28 | Mechanical stepless transmission gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS591861A true JPS591861A (en) | 1984-01-07 |
Family
ID=14516932
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10969882A Pending JPS591861A (en) | 1982-06-28 | 1982-06-28 | Mechanical stepless transmission gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS591861A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016109551A1 (en) * | 2016-05-24 | 2017-11-30 | Volkswagen Aktiengesellschaft | Stepped planetary gear |
-
1982
- 1982-06-28 JP JP10969882A patent/JPS591861A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016109551A1 (en) * | 2016-05-24 | 2017-11-30 | Volkswagen Aktiengesellschaft | Stepped planetary gear |
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