JPS6199760A - Toroidal type continuously variable transmission - Google Patents
Toroidal type continuously variable transmissionInfo
- Publication number
- JPS6199760A JPS6199760A JP22027284A JP22027284A JPS6199760A JP S6199760 A JPS6199760 A JP S6199760A JP 22027284 A JP22027284 A JP 22027284A JP 22027284 A JP22027284 A JP 22027284A JP S6199760 A JPS6199760 A JP S6199760A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- planetary gear
- toroidal
- output
- input
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
-
- 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
- F16H15/32—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 curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—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 curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—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 curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
-
- 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
- F16H37/086—CVT using two coaxial friction members cooperating with at least one intermediate friction member
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
Description
【発明の詳細な説明】
発明の分野
本発明は自動車用変速機として好適なトロイダル形無段
変速機に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a toroidal continuously variable transmission suitable as an automobile transmission.
従来技術とその問題点
従来、特公昭４７−１２４２号公報に示されるように、
同一軸線上に配置された入出力ディスクの対向面にそれ
ぞれ円環溝を設け、該円環溝の間に複数のローラを配置
してなるトロイダル変速部と、第１．第２の係合駆動装
置とを備え、上記ローラの傾斜角を変えることによって
、減速から増速に至るあらゆる変速と前後進の切り換え
と中立状態とを実現できるようにしたトロイダル形無段
変速機が知られている。Conventional technology and its problems Conventionally, as shown in Japanese Patent Publication No. 1242-1987,
a toroidal transmission section comprising annular grooves provided on opposing surfaces of input and output disks disposed on the same axis, and a plurality of rollers disposed between the annular grooves; A toroidal continuously variable transmission comprising a second engagement drive device and capable of realizing all speed changes from deceleration to speed increase, switching between forward and backward movement, and a neutral state by changing the inclination angle of the roller. It has been known.
このトロイダル形無段変速機においては、ローラの傾斜
角を制御するだけで上記のあらゆる状態を実現できるた
め、減速機構や前後進切換機構、さらにはニュートラル
状態を得るための発進用クラッチが不要になるという多
大の効果を有している。This toroidal continuously variable transmission can achieve all of the above states simply by controlling the inclination angle of the rollers, eliminating the need for a speed reduction mechanism, a forward/reverse switching mechanism, or even a starting clutch to obtain a neutral state. It has a great effect of becoming.
ところが、上記の無段変速機の場合には第１と第２の保
合駆動装置が必要であり、これらの構造、特に第１入力
結合部と第２入力結合部とを存する第２係合駆動装置の
構造が複雑であり、全体として大型化するとともに高価
となるという欠点があった・
発明の目的
本発明はかかる従来の問題点に鑑みてなされたもので、
その目的は、ローラの傾きを変えるだけで無段階の変速
と前後進の切り換えと中立状態とを実現でき、かつ構造
の極めて簡単なトロイダル形無段変速機を提供すること
にある。However, in the case of the above-mentioned continuously variable transmission, first and second locking drive devices are required, and these structures, especially the second engagement including the first input coupling portion and the second input coupling portion, are required. The structure of the drive device is complicated, and the disadvantage is that it becomes large and expensive as a whole.Objective of the InventionThe present invention has been made in view of these conventional problems.
The purpose is to provide a toroidal continuously variable transmission which is capable of realizing stepless speed change, switching between forward and backward movement, and a neutral state by simply changing the inclination of the rollers, and which has an extremely simple structure.
発明の構成
上記目的を達成するために、本発明は・、トロイダル変
速部の入力ディスクと連結された入力部材にｆｉ星歯車
列のサンギヤを連結するとともに、出力ディスクにリン
グギヤを連結し、かつ上記サンギヤとリングギヤとに噛
み合うプラネタリギヤを支持するキャリヤに出力部材を
連結したものである。Structure of the Invention In order to achieve the above-mentioned object, the present invention connects the sun gear of the fi star gear train to the input member connected to the input disk of the toroidal transmission section, and connects the ring gear to the output disk, and An output member is connected to a carrier that supports a planetary gear that meshes with a sun gear and a ring gear.
すなわち、トロイダル変速部と遊星歯車列とを組み合わ
せ、サンギヤ入力、キャリヤ出力とする１・
ことにより・無段階０変速と前後進０切り換えと
中立状態とを実現できるようにしたものである。In other words, a 1.
By doing so, it is possible to realize stepless 0-shifting, forward/reverse 0 switching, and neutral state.
実施例の説明
第１図は本発明にかかるトロイダル形無段変速機をＦＦ
式あるいはＲＲ式自動車に通用した一例を示し、エンジ
ン１と連結された入力軸（入力部材）２の途中には、遊
星歯車列ｌＯのサンギヤｌｌが固定されており、この入
力軸２の端部にはトロイダル変速部３の入力ディスク４
が連結されている。DESCRIPTION OF EMBODIMENTS FIG. 1 shows a toroidal continuously variable transmission according to the present invention.
This shows an example that is applicable to type or RR type automobiles.A sun gear 11 of a planetary gear train 10 is fixed in the middle of an input shaft (input member) 2 connected to an engine 1. is the input disk 4 of the toroidal transmission section 3.
are connected.
トロイダル変速部３は周知のとおり、同一軸線上に配置
された入力ディスク４および出力ディスク５と、両ディ
スク４．５の対向面に形成した円環１４ａ、５ａの間に
配置した複数のローラ６とで構成されており、上記ロー
ラ６を紙面に垂直な支軸６ａを中心に傾動させることに
より、入出力ディスク４．５の有効径が変化し、変速比
を無段階に変化させることができる。上記出力ディスク
５は入力ディスク４に対しエンジン１側に配置されてお
り、この出力ディスク５の背面中央には上記入力軸２の
外周に回動自在に挿通された従動軸７が連結されている
。As is well known, the toroidal transmission section 3 includes an input disk 4 and an output disk 5 arranged on the same axis, and a plurality of rollers 6 arranged between rings 14a and 5a formed on opposing surfaces of both disks 4.5. By tilting the roller 6 about a support shaft 6a perpendicular to the plane of the paper, the effective diameter of the input/output disk 4.5 changes, and the gear ratio can be changed steplessly. . The output disk 5 is arranged on the engine 1 side with respect to the input disk 4, and a driven shaft 7, which is rotatably inserted through the outer periphery of the input shaft 2, is connected to the center of the back surface of the output disk 5. .
上記従動軸７の端部は遊星歯車列１０のリングギヤ１２
と連結されており、このリングギヤ１２とサンギヤ１１
との間には、第２図に示すように３個のプラネタリギヤ
１３が噛み合い自在に配置されている。そして、３個の
プラネタリギヤ１３はキャリヤ１４によって相互に連結
され、このキャリヤ１４は出力歯車１６と出力軸（出力
部材）１５を介して連結されている。The end of the driven shaft 7 is connected to the ring gear 12 of the planetary gear train 10.
The ring gear 12 and sun gear 11
As shown in FIG. 2, three planetary gears 13 are disposed so as to be able to freely mesh with each other. The three planetary gears 13 are connected to each other by a carrier 14, and this carrier 14 is connected to an output gear 16 via an output shaft (output member) 15.
上記出力歯車１６はディファレンシャル装置１７の歯車
１８と直接噛み合っており、動力をアクスルシャフト１
９に伝達するように構成されている。The output gear 16 directly meshes with the gear 18 of the differential device 17, and transmits power to the axle shaft 1.
9.
つぎに、上記構成のトロイダル形無段変速機の作動につ
いて具体的に説明する。Next, the operation of the toroidal continuously variable transmission having the above configuration will be specifically explained.
表、ｌは、例えば遊星歯車列１０のサンギヤ１１の歯数
を３６．リングギヤ１２の歯数を８４゜プラネタリギヤ
１３の歯数を２３とした場合における各ギヤの回転数、
トロイダル変速部の変速比Ｉｔ （−サンギヤの回転
数÷リングギヤの回転数）、全体の変速比１ａ （−
サンギヤの回転数十キャリヤの回転数）を相対運動の重
ね合わせによる方法で求めたものである。Table 1 shows, for example, the number of teeth of the sun gear 11 of the planetary gear train 10, 36. The number of rotations of each gear when the number of teeth of the ring gear 12 is 84 degrees and the number of teeth of the planetary gear 13 is 23,
Gear ratio It of toroidal gearbox (-Sun gear rotation speed ÷ Ring gear rotation speed), overall gear ratio 1a (-
The number of rotations of the sun gear (the number of rotations of the carrier) was determined by a method based on the superposition of relative motions.
表、１から明らかなように、トロイダル変速部の変速比
Ｉｔを−２，３３とした場合には、全体の変速比１ａは
無限大、すなわちキャリヤ出力が零となってニュートラ
ル状態となり、トロイダル変速部の変速比Ｉ【を−０．
５３とした場合には、全体の変速比１ａは−０，９１と
なって増速前進となり、トロイダル変速部の変速比ｒｔ
を−１とした場合には、全体の変速比１ａは−２，５と
なって減速前進となり、さらにトロイダル変速部の変速
比Ｉｔを−２，７８とした場合には、全体の変速比１ａ
は２０となって減速後退となる。As is clear from Table 1, when the gear ratio It of the toroidal transmission section is set to -2, 33, the overall gear ratio 1a is infinite, that is, the carrier output becomes zero and becomes a neutral state, and the toroidal transmission The gear ratio I [-0.
53, the overall gear ratio 1a becomes -0.91, resulting in accelerated forward movement, and the gear ratio rt of the toroidal transmission section
When is set to -1, the overall gear ratio 1a becomes -2.5, resulting in deceleration and forward movement. Furthermore, when the gear ratio It of the toroidal transmission section is set to -2,78, the overall gear ratio 1a becomes -2.5.
becomes 20, resulting in deceleration and retreat.
第３図はこのようにして求めたトロイダル変速部の変速
比Ｉｔと全体の変速比１ａとの関係を示すグラフである
０通常のトロイダル変速部の場合、変速比Ｉｔはほぼ０
．２５〜４．０の範囲にあるので、この範囲内において
全体の変速比１ａを０．９〜ψの範囲で自在に変えるこ
とができることがわかる。なお、サンギヤ１１．リング
ギヤ１２およびプラネタリギヤ１３の歯数は任意に変更
可能であるため、変速比！ｔとＩａとの関係も自在に変
えることができる。FIG. 3 is a graph showing the relationship between the gear ratio It of the toroidal transmission section obtained in this way and the overall gear ratio 1a.0 In the case of a normal toroidal transmission section, the gear ratio It is approximately 0.
．． Since it is in the range of 25 to 4.0, it can be seen that within this range, the overall gear ratio 1a can be freely changed in the range of 0.9 to ψ. In addition, sun gear 11. Since the number of teeth of the ring gear 12 and planetary gear 13 can be changed arbitrarily, the gear ratio! The relationship between t and Ia can also be changed freely.
上記のように、トロイダル変速部の変速比を変える、す
なわちローラ６の傾斜角を変えることにより、発進から
増速までのすべての変速を実現でき、かつ前後進の切り
換えと中立状態を得ることもできる。したがって、トロ
イダル変速部のみでは不充分な減速比を補うための減速
機構や、前後適切ＴＩ８機構、さらには発進用クラッチ
などが不要となり、構造を極めて簡素化できる。また、
トロイダル変速部の変速比を調節して全体の変速比が極
めて大きな値、すなわち大減速となるようにすれば、言
わばエンジンブレーキが過大となった状態となり、これ
でブレーキを代用することも可能である。As mentioned above, by changing the gear ratio of the toroidal transmission section, that is, by changing the inclination angle of the roller 6, all speed changes from starting to increasing speed can be realized, and it is also possible to switch between forward and backward movement and obtain a neutral state. can. Therefore, a reduction mechanism for compensating for an insufficient reduction ratio with only the toroidal transmission section, a proper front and rear TI8 mechanism, a starting clutch, etc. are not required, and the structure can be extremely simplified. Also,
If the gear ratio of the toroidal transmission section is adjusted so that the overall gear ratio becomes an extremely large value, that is, a large deceleration, the engine brake becomes excessive, so to speak, and this can also be used as a brake. be.
上記実施例では、遊星歯車列１０をエンジンｌとトロイ
ダル変速部３との間に配置し、ＦＦ式あるいはＲＲ式の
自動車用変速機として好適な構造を示したが、これに限
らず、第４図に示すように遊星歯車列１０をトロイダル
変速部３に対しエンジン１とは反対側に配置してもよい
。In the above embodiment, the planetary gear train 10 is arranged between the engine 1 and the toroidal transmission section 3, and a structure suitable for an FF or RR type automobile transmission is shown, but the structure is not limited to this. As shown in the figure, the planetary gear train 10 may be arranged on the opposite side of the toroidal transmission section 3 from the engine 1.
また、上記実施例の遊星歯車列１０としてシンプソン形
のものを示したが、これに限らず、あらゆる形式のＭ星
歯車列を使用できることは勿論である。Furthermore, although a Simpson-type planetary gear train 10 is shown as the planetary gear train 10 in the above embodiment, it goes without saying that the invention is not limited to this, and any type of M-star gear train can be used.
発明の効果
以上の説明で明らかなように、本発明によればトロイダ
ル変速部のローラの傾斜角を調整だけで、発進から増速
までのすべての変速が可能となるとともに、前後進の切
り換えと中立状態の実現も可能となる。しかも、トロイ
ダル変速部の入力ディスクと遊星歯車列のサンギヤとを
連結し、出力ディスクとリングギヤとを連結し、プラネ
タリギヤを支持したキャリヤから出力するという極めて
簡単な構造としたので、装置を小型軽量化できるととも
に、安価に構成できる。Effects of the Invention As is clear from the above explanation, according to the present invention, by simply adjusting the inclination angle of the rollers of the toroidal transmission section, all speed changes from starting to speed increase are possible, as well as switching between forward and backward movement. It also becomes possible to realize a neutral state. Furthermore, the input disk of the toroidal transmission unit is connected to the sun gear of the planetary gear train, the output disk is connected to the ring gear, and the output is output from the carrier that supports the planetary gear, making the device smaller and lighter. It can be constructed at low cost.
第１図は本発明にかかるトロイダル形無段変速機の一例
の概略構成図、第２図は遊星歯車列の構成を示す概略側
面図、第３図はトロイダル変速部の変速比と全体の変速
比との関係を示す図、第４図はトロイダル形無段変速機
の他の例の概略構成図である。
■・・・エンジン、２・・・入力軸、３・・・トロイダ
ル変速部、４・・・入力ディスク、５・・・出力ディス
ク、４ａ、５ａ・・・円環溝、６・・・ローラ、ｌＯ・
・・遊星歯車列、ｌｌ・・・サンギヤ、１２・・・リン
グギヤ、１３・・・プラネタリギヤ、１４・・・キャリ
ヤ、１５・・・出力軸、１６・・・出力歯車、１７・・
・ディファレンシャル装置。
出 願 人 ダイハツ工業株式会社
代 理 人 弁理士 筒井 秀隆
第１図
第２図
第３図
第４図FIG. 1 is a schematic configuration diagram of an example of a toroidal continuously variable transmission according to the present invention, FIG. 2 is a schematic side view showing the configuration of a planetary gear train, and FIG. 3 is a diagram showing the gear ratio of the toroidal transmission section and the overall transmission. FIG. 4, which is a diagram showing the relationship with the ratio, is a schematic configuration diagram of another example of a toroidal continuously variable transmission. ■... Engine, 2... Input shaft, 3... Toroidal transmission section, 4... Input disk, 5... Output disk, 4a, 5a... Annular groove, 6... Roller , lO・
... Planetary gear train, ll ... Sun gear, 12 ... Ring gear, 13 ... Planetary gear, 14 ... Carrier, 15 ... Output shaft, 16 ... Output gear, 17 ...
・Differential device. Applicant Daihatsu Motor Co., Ltd. Agent Patent Attorney Hidetaka Tsutsui Figure 1 Figure 2 Figure 3 Figure 4
Claims (1)
にそれぞれ円環溝を設け、該円環溝の間に複数のローラ
を配置してなるトロイダル変速部を備えたトロイダル形
無段変速機において、上記トロイダル変速部の入力ディ
スクと連結された入力部材に遊星歯車列のサンギヤを連
結するとともに、出力ディスクにリングギヤを連結し、
かつ上記サンギヤとリングギヤとに噛み合うプラネタリ
ギヤを支持するキャリヤに出力部材を連結したことを特
徴とするトロイダル形無段変速機。(1) A toroidal type continuously variable transmission equipped with a toroidal transmission section in which annular grooves are provided on opposing surfaces of input and output disks arranged on the same axis, and a plurality of rollers are arranged between the annular grooves. In the machine, a sun gear of a planetary gear train is connected to an input member connected to an input disk of the toroidal transmission section, and a ring gear is connected to an output disk,
A toroidal continuously variable transmission characterized in that an output member is connected to a carrier that supports a planetary gear meshing with the sun gear and the ring gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22027284A JPS6199760A (en) | 1984-10-18 | 1984-10-18 | Toroidal type continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22027284A JPS6199760A (en) | 1984-10-18 | 1984-10-18 | Toroidal type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6199760A true JPS6199760A (en) | 1986-05-17 |
| JPH0522095B2 JPH0522095B2 (en) | 1993-03-26 |
Family
ID=16748572
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22027284A Granted JPS6199760A (en) | 1984-10-18 | 1984-10-18 | Toroidal type continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6199760A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2015527552A (en) * | 2012-09-07 | 2015-09-17 | デーナ リミテッド | Ball CVT with output connection power path |
| CN106715179A (en) * | 2014-07-30 | 2017-05-24 | 传输Cvt股份有限公司 | Driveline for off-highway vehicles provided with a dual function cvt |
| WO2019234812A1 (en) * | 2018-06-05 | 2019-12-12 | 株式会社ユニバンス | Continuously variable transmission |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07124578A (en) * | 1993-11-01 | 1995-05-16 | Kirin Brewery Co Ltd | Biomembrane filter tank |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5747063A (en) * | 1980-05-31 | 1982-03-17 | Biieru Tekunorojii Ltd | Speed change machine |
| JPS5965659A (en) * | 1982-10-04 | 1984-04-13 | Nissan Motor Co Ltd | Power transmission device |
-
1984
- 1984-10-18 JP JP22027284A patent/JPS6199760A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5747063A (en) * | 1980-05-31 | 1982-03-17 | Biieru Tekunorojii Ltd | Speed change machine |
| JPS5965659A (en) * | 1982-10-04 | 1984-04-13 | Nissan Motor Co Ltd | Power transmission device |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2015527552A (en) * | 2012-09-07 | 2015-09-17 | デーナ リミテッド | Ball CVT with output connection power path |
| CN106715179A (en) * | 2014-07-30 | 2017-05-24 | 传输Cvt股份有限公司 | Driveline for off-highway vehicles provided with a dual function cvt |
| WO2019234812A1 (en) * | 2018-06-05 | 2019-12-12 | 株式会社ユニバンス | Continuously variable transmission |
| JPWO2019234812A1 (en) * | 2018-06-05 | 2021-06-17 | 株式会社ユニバンス | Continuously variable transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0522095B2 (en) | 1993-03-26 |
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