JPS6350583B2 - - Google Patents
Info
- Publication number
- JPS6350583B2 JPS6350583B2 JP55031180A JP3118080A JPS6350583B2 JP S6350583 B2 JPS6350583 B2 JP S6350583B2 JP 55031180 A JP55031180 A JP 55031180A JP 3118080 A JP3118080 A JP 3118080A JP S6350583 B2 JPS6350583 B2 JP S6350583B2
- Authority
- JP
- Japan
- Prior art keywords
- axis
- rotating friction
- rotation
- transmission
- rolling
- 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 34
- 238000005096 rolling process Methods 0.000 claims description 25
- 238000001514 detection method Methods 0.000 claims description 7
- 230000033001 locomotion Effects 0.000 claims description 2
- 239000010687 lubricating oil Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
Landscapes
- Friction Gearing (AREA)
- Control Of Transmission Device (AREA)
Description
【発明の詳細な説明】
本発明は例えば動力舵取装置用ポンプ、クーラ
用コンプレツサ、エアポンプのごとき自動車付属
装置を、自動車エンジンの速度変動にかかわりな
く実質的に一定の速度で駆動するための無段変速
機に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention is a system for driving an automobile accessory device such as a power steering pump, a cooler compressor, or an air pump at a substantially constant speed regardless of speed fluctuations of an automobile engine. This relates to a gear transmission.
本発明の目的とするところは、構造が簡単かつ
小型でしかも信頼性を備えた無段変速機を提供す
ることである。 An object of the present invention is to provide a continuously variable transmission that is simple in structure, compact, and reliable.
一般に無段変速機の速度検出手段としては遠心
ガバナ装置が多くもちいられている。かかる遠心
ガバナ装置は、遠心力によつて半径方向に変位す
るボールを備えており、かかるボールを組込むに
は変速機の構成が大型化し、しかもこの遠心力は
エンジン回転数の２乗に比例する関係をもつてい
るため、非線型特性をもつた制御ばねを組込む等
特殊の構造にしないと定速制御ができない欠点が
あつた。また外部に速度検出手段を設けるものは
出力導入用の圧力配管を必要とし、ジヨイント部
のシールあるいは変速機内部の潤滑オイルとの混
合防止を行なわなければならず、構成が複雑化
し、これによつて信頼性が低下する欠点があつ
た。 Generally, a centrifugal governor device is often used as a speed detection means for a continuously variable transmission. Such a centrifugal governor device is equipped with a ball that is displaced in the radial direction by centrifugal force, and incorporating such a ball requires an enlarged transmission structure, and furthermore, this centrifugal force is proportional to the square of the engine rotation speed. Because of this relationship, there was a drawback that constant speed control could not be achieved without a special structure such as incorporating a control spring with nonlinear characteristics. In addition, devices with external speed detection means require pressure piping for introducing the output, and must be sealed at the joint or prevented from mixing with the lubricating oil inside the transmission, making the configuration complicated. However, there was a drawback that reliability decreased.
本発明は従来のこのような欠点を解消するため
になされたもので、以下本発明の実施例を図面に
基づいて説明する。第１図において１０は変速機
ケースで、自動車エンジン１１に取付られた取付
基板１２ならびにこの取付基板１２に固定された
ハウジング１３より構成されている。この変速機
ケース１０内には一対の回転摩擦板１４，１５が
収容され、この一方の回転摩擦板１４は変速機ケ
ース１０内に突入する自動車エンジン１１のクラ
ンク軸１６に楔止され、またもう一方の回転摩擦
板１５は前記変速機ケース１０内に軸受１７によ
つて前記クランク軸１６の軸線と一致する変速機
軸線を中心として回転可能に軸承されている。さ
らに変速機ケース１０内には軸受１８によつて前
記変速機軸線を中心として出力部材１９が回転可
能に軸承されている。この出力部材１９はその一
端を前記回転摩擦板１５と対向され、その対向面
間には加圧機構２０が介挿されている。この加圧
機構２０は第３図に示すように傾斜面２１ａ，２
２ａを有する一対の係合プレート２１，２２と、
係合ボール２３より構成され、例えば出力部材１
９に対して回転摩擦板１５が相対回転すると、係
合ボール２３は傾斜面２１ａ，２２ａにくいつ
き、これによつて回転摩擦板１５に軸方向加圧力
を付与し、同時に両者を一体化するようになつて
いる。前記出力部材１９はその他端を変速機ケー
ス１０の外方へ突出され、その先端にはプーリ２
４が固着されている。このプーリ２４にはベルト
が巻張られ、例えば動力舵取用ポンプ、クーラ用
コンプレツサ、エアポンプのような自動車用付属
装置に回転を伝えるようになつている。 The present invention has been made to overcome these conventional drawbacks, and embodiments of the present invention will be described below with reference to the drawings. In FIG. 1, reference numeral 10 denotes a transmission case, which is comprised of a mounting board 12 attached to an automobile engine 11 and a housing 13 fixed to this mounting board 12. A pair of rotating friction plates 14 and 15 are housed in the transmission case 10, and one of the rotating friction plates 14 is wedged to the crankshaft 16 of the automobile engine 11 that enters the transmission case 10. One rotary friction plate 15 is rotatably supported in the transmission case 10 by a bearing 17 about a transmission axis that coincides with the axis of the crankshaft 16 . Furthermore, an output member 19 is rotatably supported within the transmission case 10 by a bearing 18 about the transmission axis. This output member 19 has one end opposed to the rotating friction plate 15, and a pressure mechanism 20 is interposed between the opposing surfaces. This pressurizing mechanism 20 has inclined surfaces 21a and 2 as shown in FIG.
A pair of engagement plates 21 and 22 having 2a,
For example, the output member 1
When the rotating friction plate 15 rotates relative to the rotating friction plate 15, the engagement balls 23 grip the inclined surfaces 21a and 22a, thereby applying an axial pressing force to the rotating friction plate 15, and simultaneously integrating the two. It's getting old. The other end of the output member 19 is projected outward from the transmission case 10, and a pulley 2 is attached to the tip of the output member 19.
4 is fixed. A belt is wound around the pulley 24, and the rotation is transmitted to an accessory device for the automobile, such as a power steering pump, a cooler compressor, or an air pump.
前記一対の回転摩擦板１４，１５間には一定の
空間２５が形成され、この空間２５には転動ボー
ル２６が円周方向に適当間隔をおいて配置されて
いる。この転動ボール２６は前記一対の回転摩擦
板１４，１５に形成された転動面１４ａ，１５ａ
に接触し、一方の回転摩擦板１４より他方の回転
摩擦板１５へ回転を伝達するようになつている。 A certain space 25 is formed between the pair of rotating friction plates 14 and 15, and rolling balls 26 are arranged in this space 25 at appropriate intervals in the circumferential direction. The rolling balls 26 are formed on rolling surfaces 14a and 15a formed on the pair of rotating friction plates 14 and 15.
The rotating friction plate 14 on one side contacts the rotating friction plate 15 on the other side to transmit rotation.
さらに前記一対の回転摩擦板１４，１５間には
前記変速機ケース１０と一体をなす保持ケース２
７が配置されている。この保持ケース２７には各
転動ボール２６の両側で回転摩擦板１４，１５の
回転軸線と平行な軸線回りに円弧面２７ａが形成
され、各円弧面２７ａにケージ２８が回転摩擦板
の回転軸線を通る平面内で揺動可能に保持され、
このケージ２８には支持軸２９によつて保持ロー
ラ３０が回転可能に支持されている。この保持ロ
ーラ３０は第２図に示すように前記転動ボール２
６間に配置され、前記回転摩擦板１４，１５と協
動して転動ボール２６を回転可能に保持するよう
になつている。従つてこの保持ロール３０をケー
ジ２８とともに保持ケース２７内で傾動させた場
合、前記転動ボール２６の自転軸は変速機軸線を
通る平面内で傾斜され、転動ボール２６の自転中
心に対する回転摩擦板１４，１５の転動面１４
ａ，１５ａまでの有効半径r1，r2の比を変化でき
るようになつている。 Furthermore, a holding case 2 integrally formed with the transmission case 10 is provided between the pair of rotating friction plates 14 and 15.
7 is placed. In this holding case 27, arcuate surfaces 27a are formed around axes parallel to the rotational axes of the rotating friction plates 14 and 15 on both sides of each rolling ball 26, and a cage 28 is formed on each of the circular arcuate surfaces 27a along the rotational axes of the rotating friction plates. is held swingably in a plane passing through the
A holding roller 30 is rotatably supported by the cage 28 by a support shaft 29. This holding roller 30 is connected to the rolling ball 2 as shown in FIG.
6, and cooperates with the rotating friction plates 14 and 15 to rotatably hold the rolling ball 26. Therefore, when this holding roll 30 is tilted together with the cage 28 within the holding case 27, the axis of rotation of the rolling balls 26 is inclined within a plane passing through the transmission axis, and rotational friction with respect to the center of rotation of the rolling balls 26 is caused. Rolling surface 14 of plates 14, 15
The ratio of the effective radii r 1 and r 2 up to a and 15a can be changed.
一方前記保持ケース２７の中央部分には変速用
シリンダ装置３１が固定されている。この変速用
シリンダ装置３１はシリンダ３２を有し、このシ
リンダ３２にはスプリング３３によつて一方向に
押圧されたピストン３４が変速機軸線方向に摺動
可能に嵌合されている。このピストン３４は両側
へ延びるピストンロツド３５，３６を有し、この
一方のピストンロツド３５には前記シリンダ３２
内へ圧力流体を導入する通路３７が形成され、他
方のピストンロツド３６には引掛け部材３８が固
定されている。この引掛け部材３８の外周はケー
ジ２８を跨ぐように二股形状になつており、各股
は前記ケージ２８に突設されたピン３８を挟みこ
むようにフオーク形状に形成されている。前記ピ
ン３８はケージ２８と保持ローラ３０の回転軸線
と互いに直交してケージ２８に取り付けられてい
る。引掛け部材３８を進退させることによつてこ
のケージ２８を変速機軸線を通る平面内で傾動さ
せるようになつている。 On the other hand, a shift cylinder device 31 is fixed to the central portion of the holding case 27. This transmission cylinder device 31 has a cylinder 32, and a piston 34 pressed in one direction by a spring 33 is fitted into the cylinder 32 so as to be slidable in the axial direction of the transmission. This piston 34 has piston rods 35 and 36 extending to both sides, and one piston rod 35 has the cylinder 32.
A passage 37 is formed into which pressure fluid is introduced, and a hook member 38 is fixed to the other piston rod 36. The outer periphery of the hook member 38 is bifurcated so as to straddle the cage 28, and each fork is formed in a fork shape so as to sandwich a pin 38 protruding from the cage 28. The pin 38 is attached to the cage 28 so as to be perpendicular to the rotation axes of the cage 28 and the holding roller 30. By moving the hook member 38 back and forth, the cage 28 is tilted within a plane passing through the transmission axis.
前記変速用シリンダ装置３１の一端には出力部
材１９の回転に応じた圧力を発生する速度検出用
ポンプ装置４０が組付られている。このポンプ装
置４０はケーシング４１を有し、このケーシング
４１には前記変速機軸線に対して所定量偏心した
内孔４２が形成されている。この内孔４２には第
４図に示すようにｎ個の内接歯を形成したアウタ
ロータ４３ならびにｎ−１個の外接歯を形成した
インナロータ４４がその側方よりケーシング側面
ならびにサイドプレート４５によつてはさまれた
状態で収納され、このインナロータ４３は前記出
力部材１９上に植設された駆動シヤフト４６上に
係止されている。前記ケーシング側面には第５図
に示すように通孔４７と連通する吸入ポート４８
ならびに絞り４９と連通する吐出ポート５０が形
成され、これら吸入ポート４８ならびに吐出ポー
ト５０を介して前記変速機ケース１０内の潤滑オ
イルを吸排するようになつている。一方サイドプ
レート４５には前記導入通路３７と通じる連通路
５１が形成され、前記ポンプ装置４０において発
生した背圧を前記変速用シリンダ装置３１に導入
するようになつている。なお６０は初期駆動用の
加圧力を付与するための皿ばねである。 A speed detection pump device 40 that generates pressure according to the rotation of the output member 19 is attached to one end of the speed change cylinder device 31. This pump device 40 has a casing 41, and an inner hole 42 is formed in the casing 41 and is eccentric by a predetermined amount with respect to the transmission axis. As shown in FIG. 4, in this inner hole 42, an outer rotor 43 having n internal teeth and an inner rotor 44 having n-1 external teeth are inserted from the sides of the casing side surface and the side plate 45. The inner rotor 43 is housed in a pinched state, and is locked onto a drive shaft 46 planted on the output member 19. As shown in FIG. 5, a suction port 48 communicating with the through hole 47 is provided on the side surface of the casing.
A discharge port 50 communicating with the throttle 49 is also formed, and the lubricating oil in the transmission case 10 is sucked and discharged through the suction port 48 and the discharge port 50. On the other hand, a communication passage 51 is formed in the side plate 45 and communicates with the introduction passage 37, so that the back pressure generated in the pump device 40 is introduced into the transmission cylinder device 31. Note that 60 is a disc spring for applying pressure for initial driving.
次に上記構成における本発明装置の作動を説明
すると、自動車エンジン１１の回転はクランク軸
１６より一対の回転摩擦板１４，１５、加圧機構
２０、出力部材１９およびプーリ２４を介して図
略の自動車用付属装置に伝えられる。同時にこの
回転は駆動シヤフト４６を介して速度検出用ポン
プ装置４０のインナロータ４４に伝えられ、この
ポンプ装置４０は前記出力部材１９の回転によつ
て変速機ケース１０内の潤滑オイルを通孔４７よ
り吸入し、絞り４９より吐出する。これによりポ
ンプ装置４０内にはポンプ回転数に応じた背圧が
発生し、この背圧は連通路５１、導入通路３７を
介して変速用シリンダ装置３１のシリンダ３２内
に導入されている。 Next, to explain the operation of the device of the present invention with the above configuration, the rotation of the automobile engine 11 is transmitted from the crankshaft 16 through a pair of rotating friction plates 14 and 15, a pressure mechanism 20, an output member 19, and a pulley 24 (not shown). The information is transmitted to the automobile accessory device. At the same time, this rotation is transmitted to the inner rotor 44 of the speed detection pump device 40 via the drive shaft 46, and this pump device 40 uses the rotation of the output member 19 to supply the lubricating oil in the transmission case 10 through the hole 47. It is inhaled and expelled through the throttle 49. As a result, back pressure is generated in the pump device 40 according to the pump rotation speed, and this back pressure is introduced into the cylinder 32 of the speed change cylinder device 31 via the communication passage 51 and the introduction passage 37.
この背圧は通常スプリング３３の撥力とバラン
スしているが、エンジン回転数すなわちポンプ回
転数が変化した場合には、圧力変化を生じて前記
スプリング３３とのバランスがくずれ、その結果
ピストン３４ならびにこのピストン３４と一体を
なす引掛け部材３８は左右動される。この引掛け
部材３８の左右動によつてケージ２８およびケー
ジ２８上に回転可能に支持された保持ローラ３０
は保持ケース２７内で所定角度揺動され、その結
果前記転動ボール２６の自転軸は変速機軸線を通
る平面内で左右に傾けられる。 This back pressure is normally balanced with the repulsive force of the spring 33, but if the engine rotation speed, that is, the pump rotation speed changes, a pressure change occurs and the balance with the spring 33 is lost, and as a result, the piston 34 and A hooking member 38 that is integral with the piston 34 is moved left and right. The cage 28 and the holding roller 30 rotatably supported on the cage 28 by the horizontal movement of the hook member 38
is swung by a predetermined angle within the holding case 27, and as a result, the axis of rotation of the rolling ball 26 is tilted left and right within a plane passing through the transmission axis.
例えば自転軸が右に傾けられたときは転動ボー
ル２６の自転中心に対する回転摩擦板１４，１５
の転動面１４ａ，１５ａまでの有効半径r1は大き
くなり、反対にr2は小さくなり、これによつて変
速比は大きくなつて出力部材１９は減速される。
逆に自転軸が左に傾けられたときは転動ボール２
６の自転中心に対する回転摩擦板１４，１５の転
動面１４ａ，１５ａまでの有効半径r1は小さくな
り、反対にr2は大きくなり、これによつて変速比
は小さくなつて出力部材１９は増速される。かか
る減速あるいは増速作用によつてエンジン回転数
の増減にかかわらず出力部材１９ならびにプーリ
は一定の速度で回転され、自動車用付属装置を定
速駆動することができる。 For example, when the axis of rotation is tilted to the right, the rotating friction plates 14 and 15 with respect to the center of rotation of the rolling ball 26
The effective radius r 1 to the rolling surfaces 14a, 15a becomes larger, while r 2 becomes smaller, thereby increasing the gear ratio and decelerating the output member 19.
Conversely, when the axis of rotation is tilted to the left, rolling ball 2
The effective radius r 1 to the rolling surfaces 14a, 15a of the rotating friction plates 14, 15 with respect to the center of rotation of the rotor 6 becomes smaller, and r 2 becomes larger, thereby reducing the gear ratio and the output member 19. The speed will be increased. Due to such a deceleration or speed increase effect, the output member 19 and the pulley are rotated at a constant speed regardless of the increase or decrease in the engine speed, and the automobile accessories can be driven at a constant speed.
前記したように本発明の無段変速機は、転動ボ
ールに対応する位置を切り欠いた保持ケースを一
対の回転摩擦板間で変速機ケースの内周に取付
け、この保持ケースに各転動ボールの両側で回転
摩擦板の回転軸線と平行な軸線回りに円弧面を形
成し、各円弧面に前記変速シリンダ装置によつて
揺動される複数のケージを回転摩擦板の回転軸線
を通る平面内で揺動可能に支承し、各ケージに保
持ローラをケージの揺動軸線と直交する軸線回り
に回転可能に軸承した構成であるので、保持ロー
ラを回転可能に支承する部材が回転摩擦板の回転
方向に占めるスペースが少なくなり、保持ローラ
間の間隔を狭めることができる。この結果多数の
転動ボールを用いることができるため、一対の回
転摩擦板間での回転動力の伝達性能が向上する顕
著なる効果が得られる。 As described above, in the continuously variable transmission of the present invention, a holding case with notches corresponding to the rolling balls is attached to the inner periphery of the transmission case between a pair of rotating friction plates, and each rolling ball is attached to the holding case. A plane is formed on both sides of the ball around an axis parallel to the axis of rotation of the rotating friction plate, and a plane passing through the axis of rotation of the rotating friction plate includes a plurality of cages rocked by the speed change cylinder device on each arc plane. The holding roller is rotatably supported in each cage, and the holding roller is rotatably supported in each cage around an axis perpendicular to the cage's swinging axis. It occupies less space in the rotational direction, and the spacing between the holding rollers can be narrowed. As a result, a large number of rolling balls can be used, so that a remarkable effect of improving the transmission performance of rotational power between a pair of rotating friction plates can be obtained.
図面は本発明の実施例を示し、第１図は本発明
にかかる無段変速機を示すもので、第２図の−
線矢視断面図、第２図は第１図の−線矢視
断面図、第３図は第１図の−線矢視断面図、
第４図は第１図の−線矢視断面図、第５図は
第１図の−線矢視図である。
１０……変速機ケース、１４，１５……回転摩
擦板、１４ａ，１５ａ……転動面、２６……転動
体、３１……変速用シリンダ装置、４０……速度
検出用ポンプ装置、４８……吸入ポート、５０…
…吐出ポート、５１……連通路。
The drawings show embodiments of the present invention, and FIG. 1 shows a continuously variable transmission according to the present invention, and FIG.
2 is a sectional view taken along the - line in FIG. 1; FIG. 3 is a sectional view taken along the - line in FIG. 1;
4 is a sectional view taken along the - line in FIG. 1, and FIG. 5 is a sectional view taken along the - line in FIG. 1. DESCRIPTION OF SYMBOLS 10... Transmission case, 14, 15... Rotating friction plate, 14a, 15a... Rolling surface, 26... Rolling element, 31... Cylinder device for speed change, 40... Pump device for speed detection, 48... ...Suction port, 50...
...Discharge port, 51...Communication path.
Claims (1)
は入力軸ならびに出力軸に連結される一対の回転
摩擦板を回転可能に支承し、この一対の回転摩擦
板に形成された互いに対向する転動面間には複数
の転動ボールを回転可能に介挿し、これらの転動
ボールに転がり接触し転動ボールの自転軸を変化
させる保持ローラを設け、保持ローラの回転軸線
を回転摩擦板の回転軸線を通る平面内で回動させ
る変速シリンダ装置を設け、回転摩擦板の回転軸
線上には前記出力側回転摩擦板によつて駆動され
る速度検出用ポンプ装置を設け、この速度検出用
ポンプ装置から吐出された圧油を前記変速シリン
ダ装置へ導くようにした無段変速機において、前
記転動ボールに対応する位置を切り欠いた保持ケ
ースを一対の回転摩擦板間で変速機ケースの内周
に取付け、この保持ケースに各転動ボールの両側
で回転摩擦板の回転軸線と平行な軸線回りに円弧
面を形成し、各円弧面に前記変速シリンダ装置に
よつて揺動される複数のケージを回転摩擦板の回
転軸線を通る平面内で揺動可能に支承し、各ケー
ジに前記保持ローラをケージの揺動軸線と直交す
る軸線回りに回転可能に軸承したことを特徴とす
る無段変速機。1. A transmission case is provided, in which a pair of rotating friction plates connected to an input shaft and an output shaft are rotatably supported, and mutually opposing rolling motions formed on the pair of rotating friction plates are provided. A plurality of rolling balls are rotatably inserted between the surfaces, and a holding roller is provided that rolls into contact with these rolling balls to change the axis of rotation of the rolling balls, and the rotational axis of the holding roller is connected to the rotation of the rotating friction plate. A variable speed cylinder device that rotates within a plane passing through the axis is provided, a speed detection pump device is provided on the rotation axis of the rotating friction plate and is driven by the output side rotating friction plate, and this speed detection pump device is provided. In the continuously variable transmission, in which pressure oil discharged from the transmission cylinder is guided to the transmission cylinder device, a holding case having a cutout at a position corresponding to the rolling ball is held between a pair of rotating friction plates on the inner periphery of the transmission case. A plurality of cages are mounted on the holding case to form an arcuate surface around an axis parallel to the axis of rotation of the rotating friction plate on both sides of each rolling ball, and each arcuate surface is provided with a plurality of cages that are oscillated by the speed change cylinder device. The continuously variable transmission is characterized in that the holding roller is rotatably supported in each cage so as to be rotatable about an axis perpendicular to the pivot axis of the cage. Machine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3118080A JPS56127852A (en) | 1980-03-12 | 1980-03-12 | Stepless transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3118080A JPS56127852A (en) | 1980-03-12 | 1980-03-12 | Stepless transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS56127852A JPS56127852A (en) | 1981-10-06 |
| JPS6350583B2 true JPS6350583B2 (en) | 1988-10-11 |
Family
ID=12324241
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3118080A Granted JPS56127852A (en) | 1980-03-12 | 1980-03-12 | Stepless transmission device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS56127852A (en) |
Cited By (1)
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|---|---|---|---|---|
| WO2014069125A1 (en) * | 2012-10-31 | 2014-05-08 | トヨタ自動車株式会社 | Stepless transmission |
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|---|---|---|---|---|
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| KR20120088869A (en) | 2004-10-05 | 2012-08-08 | 폴브룩 테크놀로지즈 인크 | Continuously variable transmission |
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| US10047861B2 (en) | 2016-01-15 | 2018-08-14 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
| CN109154368B (en) | 2016-03-18 | 2022-04-01 | 福博科知识产权有限责任公司 | Continuously variable transmission, system and method |
| US10023266B2 (en) | 2016-05-11 | 2018-07-17 | Fallbrook Intellectual Property Company Llc | Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmissions |
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Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52137560A (en) * | 1976-05-12 | 1977-11-17 | Toyota Motor Corp | Non-stage change gear |
-
1980
- 1980-03-12 JP JP3118080A patent/JPS56127852A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52137560A (en) * | 1976-05-12 | 1977-11-17 | Toyota Motor Corp | Non-stage change gear |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014069125A1 (en) * | 2012-10-31 | 2014-05-08 | トヨタ自動車株式会社 | Stepless transmission |
| JP2014092175A (en) * | 2012-10-31 | 2014-05-19 | Toyota Motor Corp | Continuously variable transmission |
| CN104736893A (en) * | 2012-10-31 | 2015-06-24 | 丰田自动车株式会社 | Stepless transmission |
| CN104736893B (en) * | 2012-10-31 | 2017-04-05 | 丰田自动车株式会社 | Buncher |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS56127852A (en) | 1981-10-06 |
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