JPS62292956A - Continuously variable device - Google Patents
Continuously variable deviceInfo
- Publication number
- JPS62292956A JPS62292956A JP61136089A JP13608986A JPS62292956A JP S62292956 A JPS62292956 A JP S62292956A JP 61136089 A JP61136089 A JP 61136089A JP 13608986 A JP13608986 A JP 13608986A JP S62292956 A JPS62292956 A JP S62292956A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- planetary gear
- output shaft
- continuously variable
- clutch
- 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
- 230000005540 biological transmission Effects 0.000 claims description 53
- 230000000694 effects Effects 0.000 abstract description 6
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
Landscapes
- Transmission Devices (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
【発明の詳細な説明】
３、 発明の詳細な説明
産業上の利用分野
本発明は無段変速装置に関する、更に詳しくは、ベルト
駆動の無段変速機構と遊星歯車機構とを組合わせて構成
せられ移動用車輌の駆動軸系に取付けられる無段変速装
置に関する。[Detailed Description of the Invention] 3. Detailed Description of the Invention Industrial Application Field The present invention relates to a continuously variable transmission, and more specifically, to a continuously variable transmission that is constructed by combining a belt-driven continuously variable transmission mechanism and a planetary gear mechanism. The present invention relates to a continuously variable transmission that is attached to the drive shaft system of a moving vehicle.
従前技術とその問題点
特願昭６１−２２７５ｇ号ならびに特願昭６１−３００
９９号には、エンヂンの出力軸に直結された太陽歯車を
有する遊星歯車機構と、エンヂンの出力軸に１対の歯車
を介して一方の無段変速プーリの廻転軸を接続させたベ
ルト、駆動方式の無段変速機構とを組合わせて構成され
た無段変速装置が記載されている。また特開昭６０−１
１６９５９号公報にはエンヂンの吐力軸疋トルクコンノ
く一ターを介して太陽歯車を接続させた遊星歯車機構と
、エンヂンの出力軸にトルクコンバーターを介して入力
軸を接続させたベルト駆動方式の無段変速機構とを組合
わせて構成された車輌用無段変速装置が示されている。Previous technology and its problems Patent application No. 2275g of 1982 and Patent application No. 300 of 1981
No. 99 describes a planetary gear mechanism having a sun gear directly connected to the output shaft of an engine, a belt in which the rotating shaft of one continuously variable speed pulley is connected to the output shaft of the engine via a pair of gears, and a driving mechanism. A continuously variable transmission device configured by combining a continuously variable transmission mechanism of the above-mentioned method is described. Also, JP-A-60-1
Publication No. 16959 describes a planetary gear mechanism in which a sun gear is connected to the output shaft of the engine via a torque converter, and a belt drive system in which the input shaft is connected to the output shaft of the engine via a torque converter. A continuously variable transmission device for a vehicle configured by combining a stepped transmission mechanism is shown.
これらの特許出願の無段減速装置はエンヂンの出力の一
部を負担して遊星歯車機構に伝達するベルト、駆動方式
の無段変速機構により行われる比較的せまい範囲の変速
により遊星歯車機構の出力軸に結集される出力に増速、
減速、正転、逆転、停止など広範囲の変速を行いつるも
のである。然しなから、これらの発明に取入れられるベ
ルト、駆動方式の無段変速機構の変速比は比較的小さく
、通例は１／４程度に過ぎな（・。従って遊星歯車機構
の出力軸に結集される出力の減速には限度がある。The continuously variable speed reduction devices of these patent applications reduce the output of the planetary gear mechanism by shifting over a relatively narrow range using a belt-driven continuously variable transmission mechanism that carries a portion of the engine's output and transmits it to the planetary gear mechanism. Speed increases due to the output concentrated on the shaft,
It can perform a wide range of speed changes such as deceleration, forward rotation, reverse rotation, and stopping. However, the gear ratio of the belt-driven continuously variable transmission mechanism incorporated in these inventions is relatively small, usually only about 1/4 (. Therefore, the gear ratio is concentrated on the output shaft of the planetary gear mechanism. There are limits to output deceleration.
発明の目的
本発明の目的は、大型エンヂンに取付けられる場合にも
耐久性を低下させることなく使用できるばかりでなく、
減速比を犬＠に向上させることのできるベルト駆動方式
の無段変速機構と遊星歯車機構とを岨合わせて構成され
る動力分割型の無段変速装置を提供することにある。OBJECTS OF THE INVENTION An object of the present invention is to not only enable it to be used without reducing durability even when installed in a large engine;
To provide a power split type continuously variable transmission device configured by combining a belt drive type continuously variable transmission mechanism and a planetary gear mechanism, which can dramatically improve the reduction ratio.
本発明の以上の目的は、太、陽歯車をエンヂンの出力軸
に接続させた第１遊星歯車機構、太１陽歯車を第１遊星
歯車機構のキャリヤに接続させり／グ・ギヤの中心に出
力軸を取付けている第２遊星歯車機構、ならびに前記エ
ンヂンの出力軸に隣接する位置に据付けられ入力軸を歯
車を介して、エンヂンの出力軸に接続させ出力軸を歯車
を介し前記第１遊星歯車機構のリング・ギヤに接続させ
たベルト駆動の無段変速機構から成る動力分割型の無段
変速装置であって、前記ベルト駆動の無段変速機構が前
記入力軸に取付けられた第１変速プーリと無端ベルトを
介し該第１変速プーリに接１読される第２変速プーリと
から成る第１段変速機構と、前記第２変速プーリと同一
の廻転軸に取付けられ５第６変速プーリならび：／Ｃ，
第１変速プーリと同軸的に配列される第４変速プーリと
から成る第２段変速機構とを備え、前記第１遊星歯車機
構が単一のリング・ギヤの内面に第１遊星歯車を介し噛
合うエンヂン直結の第１太陽歯車と、第２遊星歯車を介
して噛合い且つ第１遊星歯車のモヤリヤに接続された第
２太陽歯車と、第２遊星歯車のキャリヤに取げけられた
出力軸とを備え、更に第１遊星歯車機構がリング・ギヤ
をｉ！ｌ］勤する第１ブレーキＢ１及び一方向クラッチ
ＦＷ、ならびに太陽歯車の廻転軸とリング・ギヤとの間
に挿入される第１クラツチＣ１を備え、第２遊星歯車機
構が太陽歯車を制動する第２ブレーキＢ２、遊星歯■の
モヤリヤを制動する第３ブレーキＢ３、太陽歯車と遊星
歯車のキャリヤとの間に挿入されろ第うクラッチＣ３、
ならびに第２ブレーキＢ２と第うクラッチＣ５との中間
で太陽歯車に附属する第４クラツチＣ１１を備え、ベル
ト、駆動の前記無段変速機構がその出力軸を第１遊星歯
車機構のリング・ギヤに接続する歯車と該出力軸との間
に挿入される第２クラツチＣ２を備えていることを特数
とする不発明の無段変速装置により達成される。The above-mentioned objects of the present invention are to provide a first planetary gear mechanism in which the large and positive gears are connected to the output shaft of an engine, and a first planetary gear mechanism in which the large positive gear is connected to the carrier of the first planetary gear mechanism. A second planetary gear mechanism having an output shaft attached thereto, and a second planetary gear mechanism installed at a position adjacent to the output shaft of the engine, the input shaft being connected to the output shaft of the engine via a gear, and the output shaft being connected to the first planetary gear via the gear. A power split type continuously variable transmission device comprising a belt-driven continuously variable transmission mechanism connected to a ring gear of a gear mechanism, wherein the belt-driven continuously variable transmission mechanism is attached to the input shaft. a first stage transmission mechanism comprising a pulley and a second speed change pulley connected to the first speed change pulley via an endless belt; a sixth speed change pulley attached to the same rotating shaft as the second speed change pulley; :/C,
a second-stage transmission mechanism consisting of a first transmission pulley and a fourth transmission pulley arranged coaxially, the first planetary gear mechanism meshing with the inner surface of a single ring gear via the first planetary gear. A first sun gear that is directly connected to the engine, a second sun gear that meshes with the second planetary gear and is connected to the moyariya of the first planetary gear, and an output shaft that is attached to the carrier of the second planetary gear. Furthermore, the first planetary gear mechanism operates the ring gear i! l] includes a first brake B1 and a one-way clutch FW that work, and a first clutch C1 that is inserted between the rotation axis of the sun gear and the ring gear, and a second planetary gear mechanism that brakes the sun gear. 2 brake B2, a 3rd brake B3 that brakes the planetary teeth, and a 3rd clutch C3 that is inserted between the sun gear and the planetary gear carrier.
Also, a fourth clutch C11 attached to the sun gear is provided between the second brake B2 and the first clutch C5, and the belt-driven continuously variable transmission mechanism connects its output shaft to the ring gear of the first planetary gear mechanism. This is achieved by an uninvented continuously variable transmission device which is characterized in that it includes a second clutch C2 inserted between the connecting gear and the output shaft.
発明の構成
本発明の装置の構成を添付図面に示す実施例について説
明すると次の如くである。DESCRIPTION OF THE PREFERRED EMBODIMENTS The structure of the apparatus of the present invention will be described below with reference to an embodiment shown in the accompanying drawings.
第１図を参照するに、太：明ｍ ｉｉ ６をエンヂンの
出力軸１に接続させた第１遊星歯車機構２、太陽歯車１
５を第１遊星出車機構２のキでリヤ１３に接続させリン
グ・ギヤ１６の中上へＣ出力部１５を取付けている第２
遊星歯車機構さ、ならびに前記二ンヂンの出力軸に隣接
する位置に取付けられ入力軸とエンヂンの出力軸１とを
歯車５２．３３により接続させ、出力軸を前記第１遊星
歯車機構２のリング・ギヤ７とを歯車３４，３５により
接続させたベルト駆動の無段変速機構ヰから成る移動用
車輌の無段変速装置１０が示されている。Referring to FIG. 1, a first planetary gear mechanism 2 and a sun gear 1 are connected to the output shaft 1 of the engine.
5 is connected to the rear 13 by the key of the first planetary exit mechanism 2, and the C output part 15 is attached to the middle upper part of the ring gear 16.
The input shaft and the output shaft 1 of the engine are connected by gears 52 and 33, and the output shaft is connected to the ring and the output shaft of the first planetary gear mechanism 2. A continuously variable transmission device 10 for a moving vehicle is shown, which is a belt-driven continuously variable transmission mechanism connected to a gear 7 by gears 34 and 35.
第２図に示す如く、ベルト駆動方式の無段変速機構４は
第１段変速機構２０ａと第２段変速機構２０ｂとから成
る２段直列型のもので減速比を大幅に増大させる。第１
段変速機構２０ａは入力軸２１に取付けられた第１変速
プーリ２５と、入力軸２１から所定距離を隔て十行洗取
付けられた中間軸２２に支持された第２変速プーリ２６
と、双方のプーリ２５．２６に懸けられた無端ベルト２
つとから構成される。入力軸２１は右端をセンター・ベ
ヤリング２１＋により同軸的に且つ廻転自在に支持させ
、ベヤリング２ヰに隣接する位置に、エンヂン出力軸１
上の歯車３２に噛合う歯車３３を備えている（第１図）
。第２段変速機構２０ｂは前記中間軸２２の延長部分に
取付けられる第３変速プーリ２７と、入力軸２１と同軸
的に配列せられ左端をセンター・ベヤリング２４に支持
させた出力軸２３に取付けられた第４変速プーリ２ｇと
、双方のプーリ２７．２ｇに懸けられる無端ベルト５０
とから構成される。As shown in FIG. 2, the belt-driven continuously variable transmission mechanism 4 is a two-stage serial type consisting of a first-stage transmission mechanism 20a and a second-stage transmission mechanism 20b, and greatly increases the reduction ratio. 1st
The gear shift mechanism 20a includes a first shift pulley 25 attached to an input shaft 21, and a second shift pulley 26 supported by an intermediate shaft 22 attached at a predetermined distance from the input shaft 21.
and an endless belt 2 hung on both pulleys 25 and 26.
It consists of one. The input shaft 21 has its right end coaxially and rotatably supported by a center bearing 21+, and the engine output shaft 1 is located adjacent to the bearing 21+.
It is equipped with a gear 33 that meshes with the upper gear 32 (Figure 1).
. The second-stage transmission mechanism 20b includes a third speed change pulley 27 attached to an extension of the intermediate shaft 22, and an output shaft 23 that is arranged coaxially with the input shaft 21 and whose left end is supported by a center bearing 24. 2 g of the fourth speed change pulley and an endless belt 50 that is hung around both pulleys 27.2 g.
It consists of
第１変速プーリ２５は、右端をセンター・ベヤリング２
１１に衡接させ左側ｒｃ入力軸２１を固着させた固定半
体２５ｓと、入力軸２１上のスプライン３９ａＫ＆い往
復する可動半休２５Ｈとから構成される。第４変速プー
リ２ｇは、左端をセンター・ベヤリング２４に衡接させ
右側に出力軸２３を固着させた固定半休２１（Ｓと、出
力軸２う上のスプライン３９ｂに沿い往復する可動半休
２８Ｈとから構成される。フォーク状を成すキャリヤ４
０が第１変速プーリ２５の左端にスラスト・ベヤリング
１ｌｌａを介して衡接する腕１ｊＱａと、第４変速プー
リ２８の右端にスラスト・ベヤリング４１ｂを介して衡
接する腕４ｏｂとを備えている。The first speed change pulley 25 has its right end connected to the center bearing 2.
11 and a fixed half body 25s to which the left rc input shaft 21 is fixed, and a movable half body 25H that reciprocates with a spline 39aK on the input shaft 21. The fourth speed change pulley 2g consists of a fixed half-shift 21 (S) whose left end is in contact with the center bearing 24 and an output shaft 23 fixed to the right side, and a movable half-shift 28H that reciprocates along a spline 39b above the output shaft 2. A fork-shaped carrier 4
0 is provided with an arm 1jQa that is connected to the left end of the first speed change pulley 25 through a thrust bearing 1lla, and an arm 4ob that is connected to the right end of the fourth speed change pulley 28 through a thrust bearing 41b.
キャリヤｌＩＯがＰ方向に動かされるときは第１変速プ
ーリ２５のＶ字溝５１ａの幅が拡大し、第４変速プーリ
２８のＶ字溝５１ｂの幅が縮小する。When the carrier lIO is moved in the P direction, the width of the V-shaped groove 51a of the first speed change pulley 25 increases, and the width of the V-shaped groove 51b of the fourth speed change pulley 28 decreases.
キャリヤ４０がＱ方向沈動されるときはｖ字溝５１ａ、
５１ｂの幅の関係が逆になる。中間軸２２は左端に隣接
して第２変速プーリ２６の固定半休２６８を、右端に隣
接して第３変速プーリ２７の固定半休２７Ｓを固着させ
、双方の半休２６Ｓ、２７Ｓの中間に設けられたスプラ
イン３９Ｃを備えている。スプライン３９０に？ｊい往
復する第２変速プーリ２６の可動半休２６Ｉ（と、第３
変速プーリ２７の可動半休２７Ｈとが中間軸２２に取付
けられている。２個の可動半休２６Ｈと２７Ｈとの間に
挿入されるスプリングもしくは油圧シリンダー３１が中
間軸２２に取付けられ、双方の半休２６Ｈ，２７Ｈを離
間する。When the carrier 40 is sunk in the Q direction, the V-shaped groove 51a,
The width relationship of 51b is reversed. The intermediate shaft 22 is provided with a fixed half-rest 268 of the second speed change pulley 26 adjacent to the left end, a fixed half-shut 27S of the third speed change pulley 27 adjacent to the right end, and provided between the two half-shuts 26S and 27S. Equipped with spline 39C. To spline 390? The movable half-stop 26I of the second speed change pulley 26 that reciprocates (and the third
A movable half stop 27H of the speed change pulley 27 is attached to the intermediate shaft 22. A spring or hydraulic cylinder 31 inserted between the two movable half-rests 26H and 27H is attached to the intermediate shaft 22 to separate the two half-rests 26H and 27H.
第２図に示す如く、ギヤリヤ１１０により第１変速プー
リ２５のｖｆ：溝５１ａの幅が小さく、第４変速プーリ
２ｇのｖ−ｆ−溝５１ｂの幅が大きい場合ては、変速ベ
ルト２つ、３０の長さが一定である清、乙山朋紬＞２Ｌ
−呂笛２珍まブーＩＩりＣの■φＣ４〃５２ａの幅は大
きく、第う変速プーリ２７のｖ字溝５２ｂの幅は小さく
成されている。従って第１段変速機構２０ａも第２段変
速機構２０ｂも共に減速作用を行い相乗効果を発揮する
。第１図に示す如く、ベルト駆動の無段変速装置４の出
力軸２うばセンター・ベヤリング２４に隣接する位置に
第１遊星歯車機構２のリング・ギヤ７の中心スリーブ３
６に取付けられた歯車３１４に噛合う歯車５５を備えて
いる。出力軸２３と、歯車３５との間には第２クラツチ
Ｃ２が取付けられている。第１遊星歯車機構２は単一の
リング・ギヤ７と、それぞれ第１、第２の遊星歯車９．
１１を介しリング・ギヤ７の内面歯（図示せず〕に噛合
う第１、第２の太陽歯車６．８とを備えている。太陽歯
車６は工／ヂンの出力軸１に接続せられ、太陽歯車８は
第１遊星歯車９のキャリヤ１２に接続されている。第１
遊星歯車機構２は第２遊星歯車１１のキャリヤ１３の中
心に出力軸１４を有している。第１遊星歯車機構２はリ
ング・ギヤ７の外周に対向する位置：て第１ブレーキＢ
１とワンウェイ・クラッチＦＷとを取付け１、太陽歯車
６とリング・ギヤ７との間に挿入された第１クラツチＣ
１を備えている。As shown in FIG. 2, when the gear rear 110 has a small width of the vf groove 51a of the first speed change pulley 25 and a large width of the vf groove 51b of the fourth speed change pulley 2g, two speed change belts, Kiyoshi with a constant length of 30, Otoyama Tomotsumugi > 2L
- The width of the ■φC4 52a of the Robue 2 Chinma Boo II R-C is large, and the width of the V-shaped groove 52b of the No. 1 speed change pulley 27 is small. Therefore, both the first-stage transmission mechanism 20a and the second-stage transmission mechanism 20b perform a deceleration action and exhibit a synergistic effect. As shown in FIG. 1, the center sleeve 3 of the ring gear 7 of the first planetary gear mechanism 2 is located adjacent to the output shaft 2 of the belt-driven continuously variable transmission 4 and the center bearing 24.
The gear 55 meshes with the gear 314 attached to the gear 6. A second clutch C2 is installed between the output shaft 23 and the gear 35. The first planetary gear mechanism 2 includes a single ring gear 7 and first and second planetary gears 9.
The first and second sun gears 6.8 mesh with the inner teeth (not shown) of the ring gear 7 through the gear 11.The sun gear 6 is connected to the output shaft 1 of the engine/gen. , the sun gear 8 is connected to the carrier 12 of the first planetary gear 9.
The planetary gear mechanism 2 has an output shaft 14 at the center of a carrier 13 of a second planetary gear 11 . The first planetary gear mechanism 2 is located at a position opposite to the outer periphery of the ring gear 7.
1 and the one-way clutch FW are installed 1, and the first clutch C inserted between the sun gear 6 and the ring gear 7.
1.
第２遊星歯車機構うは、左端を第１遊星歯車機構２の出
力軸１１ｉに接続させたスリーブ状の廻転軸う７を有す
る太陽歯車１５を備えている。太陽歯車１５は遊星歯車
１７を介してリング・ギヤ１６の内面の歯に噛合ってい
る。リング・ギヤ１６は中心線の位置に右側に突出する
出力軸５を備えている。遊星歯車１７のキャリヤ１８は
エンヂンの出力軸１に同軸的な廻転軸１つと、この廻転
軸に同心的な外輪３８とを備えている。第２遊星歯車機
構うは、太陽歯車１５を制動する第２ブレーキＢ２、遊
星歯車１７のキャリヤ１８を制動する第３ブレーキＢ３
、太陽歯車１５の廻転軸う７と遊星歯車１７のキャリヤ
１８の廻転軸１つとの間に挿入される第３クラツチＣ３
と、前記第２ブレーキＢ２と前記第うクラッチＣ３との
中間で廻転軸３７に附属する第４クラツチｃ４とを備え
ている。The second planetary gear mechanism includes a sun gear 15 having a sleeve-shaped rotating shaft 7 whose left end is connected to the output shaft 11i of the first planetary gear mechanism 2. Sun gear 15 meshes with teeth on the inner surface of ring gear 16 via planet gear 17. The ring gear 16 is provided with an output shaft 5 projecting to the right at the center line. The carrier 18 of the planetary gear 17 includes one rotating shaft coaxial with the output shaft 1 of the engine, and an outer ring 38 concentric with this rotating shaft. The second planetary gear mechanism includes a second brake B2 that brakes the sun gear 15 and a third brake B3 that brakes the carrier 18 of the planetary gear 17.
, a third clutch C3 inserted between the rotation shaft 7 of the sun gear 15 and one rotation shaft of the carrier 18 of the planetary gear 17;
and a fourth clutch c4 attached to the rotating shaft 37, located between the second brake B2 and the third clutch C3.
上記４個のクラッチＣ１、Ｃ２、Ｃ５，０１１１５個の
ブレーキＢ１、Ｂ２、Ｂ３及び１個のワンウェイ・クラ
ッチＦＷの作動のタイミングと位置とを制御するコンピ
ューター（図示せず）が設けられ、なめらかで静粛な変
速が行われるよう；て成されている。A computer (not shown) is provided to control the timing and position of the operation of the four clutches C1, C2, C5, 01115 brakes B1, B2, B3 and one one-way clutch FW. It is designed to ensure quiet gear shifting.
本発明の装置の各速度における作動は、前述の４個のク
ラッチと、う個のブレーキと、１個のワンウェイ・クラ
ッチとから選ばれる所定の作動要素を組合わせ使用する
ことにより行われる。スタート、無段変速、トップ、オ
ーバードライブ、逆進などの各段階で使用するクラッチ
、ブレーキなど作動要素の組合わせは次の如くである。The operation of the device of the present invention at each speed is achieved by using a combination of predetermined actuating elements selected from the aforementioned four clutches, two brakes, and one one-way clutch. The combinations of operating elements such as clutches and brakes used at each stage, such as start, continuously variable speed, top, overdrive, and reverse, are as follows.
作動状態 作動要素 変速比（４） オー
バードライブ ｃｌ、Ｃ３，Ｂ１２ ０．７
５◎ベルト駆動の無段変速機構４の変速比１／１１×１
／４−１／１６
◎第１遊星歯車機構２（変速用）の変速比１／うＸ １
１５ ： １／９
◎第２遊星歯車機構３（逆転及びオーバードライブ用）
の変速比は１／１１である。Operating condition Operating element Gear ratio (4) Overdrive cl, C3, B12 0.7
5◎Transmission ratio of belt-driven continuously variable transmission mechanism 4: 1/11 x 1
/4-1/16 ◎Transmission ratio of the first planetary gear mechanism 2 (for shifting) 1/UX 1
15: 1/9 ◎Second planetary gear mechanism 3 (for reverse rotation and overdrive)
The gear ratio is 1/11.
◎この場合、歯車３２、う５の歯数比、及び歯車う４．
３５の歯数比はそれぞれ１／２程度に選定される。◎In this case, the tooth number ratio of gear 32 and gear 5, and gear 4.
The number ratio of the 35 teeth is selected to be approximately 1/2.
以上のクラッチ、ワンウェイ・クラッチ及びブレーキを
適宜の圧力とタイム・ラグとをもって作動させ起動時や
変速時の衝撃を低減させる。各段階における各作動要素
の作動状況は次の如くである。The above-mentioned clutches, one-way clutches, and brakes are operated with appropriate pressure and time lag to reduce shocks during startup and gear changes. The operating status of each operating element at each stage is as follows.
（１）起動及び低速時
第１遊星歯車機構２のリング・ギヤ７がブレーキＢ１に
より固定されているから、太陽歯車６が廻転すると遊星
歯車９のキャリヤ１２が廻転し、第２太陽歯車８を廻転
させる、従って第２遊星歯車１１及びそのキャリヤ１５
を介し出力軸１４を廻転させろ。第２遊星歯車機構うで
はクラッチＣ３、Ｃ４が順次つながるから遊星歯車１７
は廻転せず、太陽歯車１５とリング・ギヤ１６とが一体
化して出力軸５を低速で廻転させる。(1) During startup and low speed Since the ring gear 7 of the first planetary gear mechanism 2 is fixed by the brake B1, when the sun gear 6 rotates, the carrier 12 of the planetary gear 9 rotates, causing the second sun gear 8 to rotate. to rotate, thus the second planetary gear 11 and its carrier 15
Rotate the output shaft 14 through. In the second planetary gear mechanism, clutches C3 and C4 are sequentially connected, so the planetary gear 17
does not rotate, and the sun gear 15 and ring gear 16 are integrated to rotate the output shaft 5 at a low speed.
（２ン変速時（ローからトップまで）
クラッチＣ２の作動により、ベルト、駆動方式の無段変
速機構４が第１遊星歯車機構２のリング・ギヤ７につな
がり、リング・ギヤ７の作動によりキャリヤ１２を変速
し、更：・こ第２太陽歯車８、第２遊星歯車１１及びキ
ャリヤ１５を介し出力軸１４を変速する。第２遊星歯車
機構うにおいては、廻転数の変化はない。従って出力軸
５の廻転数はベルト駆動の無段変速機構４の２本の無端
べ、１１／ ）２つ、３０の位置により左右される。(During 2-speed shifting (from low to top) The operation of the clutch C2 connects the belt-driven continuously variable transmission mechanism 4 to the ring gear 7 of the first planetary gear mechanism 2, and the operation of the ring gear 7 connects the carrier 12, and furthermore, the output shaft 14 is changed through the second sun gear 8, second planetary gear 11, and carrier 15.In the second planetary gear mechanism, there is no change in the rotation speed.Therefore, the output The number of revolutions of the shaft 5 depends on the positions of the two endless wheels, 11/2 and 30, of the belt-driven continuously variable transmission mechanism 4.
（３）最高時速（トップ）
このときはクラッチＣ１の作動により太陽歯車６とリン
グ・ギヤ７とが一体化し、遊星歯車９．１１は廻転セず
、そヤリャ１う上の出力軸１１４が太陽歯車６．８と、
即ちエンヂン出力軸１と同一の廻転数で廻転する。第２
遊星歯車機構５では廻転数の変化はなく、出力軸５がエ
ンヂンの出力軸１と同一速度で廻転する。(3) Maximum speed (top) At this time, the sun gear 6 and ring gear 7 are integrated by the operation of the clutch C1, the planetary gears 9 and 11 do not rotate, and the output shaft 114 on the top of the sun gear 1 is rotated. Gear 6.8 and
That is, it rotates at the same rotation speed as the engine output shaft 1. Second
In the planetary gear mechanism 5, the rotation speed does not change, and the output shaft 5 rotates at the same speed as the output shaft 1 of the engine.
（ｑ）増速駆動時Ｃオーバードライブ）第１遊星歯車機
構２の出力軸１４はトップの場合と同様にエンヂンの出
力軸１と同一の廻転数で廻転する。第２遊星歯車機構５
では太陽歯車１５がブレーキＢ２により固定せられ、ク
ラッチＣ３によりエンヂン出力＠１に連結されたキャリ
ヤ１８により遊星歯車１７が太陽歯車１５の外周を廻転
する。従って、エンヂンの出力軸１に直結されたキャリ
ヤ１ｇに取付げられた遊星歯車１７が太陽歯車１５のま
わりの公転と、歯車１７の自転とによりリング・ギヤ１
６即ち出力＠５が増速される。(q) C overdrive during speed-increasing drive) The output shaft 14 of the first planetary gear mechanism 2 rotates at the same rotation speed as the output shaft 1 of the engine, as in the case of the top. Second planetary gear mechanism 5
In this case, the sun gear 15 is fixed by the brake B2, and the planetary gear 17 rotates around the outer periphery of the sun gear 15 by the carrier 18, which is connected to the engine output @1 by the clutch C3. Therefore, the planetary gear 17 attached to the carrier 1g directly connected to the output shaft 1 of the engine rotates around the sun gear 15 and rotates on its axis, causing the ring gear 1
6, that is, the output @5 is accelerated.
（５）逆 進
第１遊星歯車機構２ではトップの場合と同様に第１クラ
ツチＣ１の作動により太陽歯車６とリング・ギヤ７とが
一体化し、第１、第２の遊星歯車９．１１は廻転せずキ
ャリヤ１５上の出力軸１４が太陽歯車６、即ちエンヂン
出力軸１と同一の廻転数で廻転する。第２遊星歯車うで
は遊星歯車１７のキャリヤ１８が第３ブレーキＢ５によ
り固定されており、太陽歯車１５はクラッチＣ１Ｉのつ
ながりにより第１遊星歯車機構２の出力軸１４に接続さ
れる。太陽歯車１５の廻転は遊星歯車１７を介しリング
・ギヤＸ６即ち出力軸５を逆転させる。(5) In the reverse first planetary gear mechanism 2, the sun gear 6 and ring gear 7 are integrated by the operation of the first clutch C1 as in the case of the top, and the first and second planetary gears 9 and 11 are Instead of rotating, the output shaft 14 on the carrier 15 rotates at the same rotation speed as the sun gear 6, that is, the engine output shaft 1. In the second planetary gear, the carrier 18 of the planetary gear 17 is fixed by a third brake B5, and the sun gear 15 is connected to the output shaft 14 of the first planetary gear mechanism 2 through engagement of the clutch C1I. The rotation of the sun gear 15 causes the ring gear X6, ie, the output shaft 5, to reverse rotation via the planetary gear 17.
以上と示す如く、本発明の装置はエンヂンの出力軸１に
直結された太陽歯車６を有する第１遊星歯車機構２と、
エンヂンの出力軸１に歯車を介して接続された入力軸２
１を有するベルト駆動方式の無段変速機構４とを組合わ
せ、それぞれの機構の減速作用を結集させたトルクを出
す出力軸１４に逆進及びオーバードライブ用の第２遊呈
歯車機構５を接続させたものであるが、ベルト駆動の無
段変速機構４と第１遊星歯車機構２とのそれぞれを２段
がまえの構成として減速効果を大幅に増大させる、即ち
ベルト駆動の無段変速機構４は第１及び第２段の変速機
構２Ｑ＆、２０ｋ）を直列に接続することにより減速比
を１／４Ｘ１／４＝１／１６とし、第１遊星歯車機構２
はリング・ギヤ７の内面に２組の遊星歯車９．１１を介
し２個の太陽歯車６．８を噛合わせることにより出力軸
１１１に１／３Ｘｌ／３＝ｌ／９に減速されたトルクを
出すことができる。As shown above, the device of the present invention includes a first planetary gear mechanism 2 having a sun gear 6 directly connected to the output shaft 1 of the engine,
Input shaft 2 connected to engine output shaft 1 via gears
1, and a second loose gear mechanism 5 for reverse and overdrive is connected to an output shaft 14 that outputs a torque that combines the deceleration effects of each mechanism. However, the belt-driven continuously variable transmission mechanism 4 and the first planetary gear mechanism 2 are each configured to have two stages in front of each other to greatly increase the deceleration effect, that is, the belt-driven continuously variable transmission mechanism 4 The first planetary gear mechanism 2
By meshing two sun gears 6.8 with the inner surface of the ring gear 7 through two sets of planetary gears 9.11, a torque reduced to 1/3Xl/3=l/9 is applied to the output shaft 111. I can put it out.
発明の効果
本発明の効果は、ベルト駆動の無段変速機構と遊星歯車
機構とのそれぞれを変速作用を継続して２段に行う構成
とすることにより減速効果を大幅に拡大させ移動用車輌
の変速を迅速容易６（行わせ運転機能を向上させること
である。Effects of the Invention The effects of the present invention are such that the belt-driven continuously variable transmission mechanism and the planetary gear mechanism are each configured to continuously change speeds into two stages, thereby greatly expanding the deceleration effect and improving the speed of transportation vehicles. The goal is to make gear changes quick and easy (6) and improve driving performance.
第１図は本発明の無段変速装置の構成を示す概要図、
第２図は第１図の装置の要部を示す拡大詳細図である。
１ エンヂンの出力軸 ２ 第１遊星歯車機溝５
第２遊星９車機構
４ ベルト葛動方式つ無段変速機構
５ 出力軸 ６ 太陽歯車７ リング
・ギヤ ８ 第２太陽歯車９ 遊星歯車
１０ 本発明の装置１１ 第２遊星歯車
１２ キャリヤ１５ キャリヤ
１４ 出力軸１５ 太陽歯車 １６ リン
グ・ギヤ１７ 遊星歯車 １ｇ キャリヤ
１つ 廻転軸 ２０ａ第１段変速機構２
０ｂ第２段変速機構 ２１ 人力軸２２ 中間＠
２３ 出力軸２４ センター・ベアリ
ング ２５ 第１変速プーリ２６ 第２変速プーリ
２７ 第う変速プーリ２ｇ 第４変速プーリ
２９ 無端ベルトう０ 無端ベルトFIG. 1 is a schematic diagram showing the configuration of the continuously variable transmission device of the present invention, and FIG. 2 is an enlarged detailed view showing the main parts of the device in FIG. 1 Engine output shaft 2 First planetary gear machine groove 5
Second planetary nine-wheel mechanism 4 Continuously variable transmission mechanism with belt sliding mechanism 5 Output shaft 6 Sun gear 7 Ring gear 8 Second sun gear 9 Planetary gear
10 Device of the present invention 11 Second planetary gear
12 Carrier 15 Carrier
14 Output shaft 15 Sun gear 16 Ring gear 17 Planetary gear 1g 1 carrier Rotating shaft 20a 1st stage transmission mechanism 2
0b 2nd stage transmission mechanism 21 Human power shaft 22 Intermediate @
23 Output shaft 24 Center bearing 25 First speed change pulley 26 Second speed change pulley
27 4th speed change pulley 2g 4th speed change pulley
29 Endless belt 0 Endless belt
Claims (1)
機構、太陽歯車を第１遊星歯車機構のキヤリヤに接続さ
せリング・ギヤの中心に出力軸を取付けている第２遊星
歯車機構、ならびに前記エンヂンの出力軸に隣接する位
置に据付けられ入力軸を歯車を介してエンヂンの出力軸
に接続させ、出力軸を歯車を介し前記第１遊星歯車機構
のリング・ギヤに接続させたベルト駆動の無段変速機構
から成る動力分割型の無段変速装置であつて、前記ベル
ト駆動の無段変速機構が前記入力軸に取付けられた第１
変速プーリと無端ベルトを介し該第１変速プーリに接続
される第２変速プーリとから成る第１段変速機構と、前
記第２変速プーリと同一の廻転軸に取付けられる第３変
速プーリならびに第１変速プーリと同軸的に配列される
第４変速プーリとから成る第２段変速機構とを備え、前
記第１遊星歯車機構が単一のリング・ギヤの内面に第１
遊星歯車を介して噛合うエンヂン直結の第１太陽歯車と
、第２の遊星歯車を介して噛合い且つ第１遊星歯車のキ
ヤリヤに接続された第２の太陽歯車と、第２遊星歯車の
キヤリヤに取付けられた出力軸とを備え、更に第１遊星
歯車機構がリング・ギヤを制動する第１ブレーキＢ１及
び一方向クラツチＦＷ、ならびに太陽歯車の廻転軸とリ
ング・ギヤとの間に挿入される第１クラツチＣ１を備え
、第２遊星歯車機構が太陽歯車を制動する第２ブレーキ
Ｂ２、遊星歯車のキヤリヤを制動する第３ブレーキＢ３
、太陽歯車と遊星歯車のキヤリヤとの間に挿入される第
３クラツチＣ３、ならびに第２ブレーキＢ２と第３クラ
ツチＣ３との中間で太陽歯車に附属する第４クラツチＣ
４を備え、前記のベルト、駆動の無段変速機構がその出
力軸を第１遊星歯車機構のリング・ギヤに接続する歯車
と該出力軸との間に挿入される第２クラツチＣ２を備え
ていることを特徴とする無段変速装置。a first planetary gear mechanism in which the sun gear is connected to the output shaft of the engine; a second planetary gear mechanism in which the sun gear is connected to the carrier of the first planetary gear mechanism and the output shaft is mounted at the center of the ring gear; A belt-driven system installed adjacent to the output shaft of the engine, with the input shaft connected to the output shaft of the engine via a gear, and the output shaft connected to the ring gear of the first planetary gear mechanism via a gear. A power split type continuously variable transmission device comprising a step-change transmission mechanism, wherein the belt-driven continuously variable transmission mechanism includes a first transmission mechanism attached to the input shaft.
a first stage transmission mechanism consisting of a speed change pulley and a second speed change pulley connected to the first speed change pulley via an endless belt; a third speed change pulley attached to the same rotating shaft as the second speed change pulley; a second-stage transmission mechanism comprising a transmission pulley and a fourth transmission pulley arranged coaxially with the transmission pulley, the first planetary gear mechanism having a first planetary gear mechanism mounted on an inner surface of a single ring gear;
A first sun gear directly connected to the engine that meshes with the planetary gear, a second sun gear that meshes with the second planetary gear and is connected to the carrier of the first planetary gear, and a carrier of the second planetary gear. A first planetary gear mechanism is further provided with a first brake B1 and a one-way clutch FW for braking the ring gear, and is inserted between the rotation axis of the sun gear and the ring gear. A second brake B2 includes a first clutch C1, and a second planetary gear mechanism brakes the sun gear, and a third brake B3 brakes the carrier of the planetary gear.
, a third clutch C3 inserted between the sun gear and the carrier of the planetary gear, and a fourth clutch C attached to the sun gear intermediate the second brake B2 and the third clutch C3.
4, and the belt-driven continuously variable transmission mechanism includes a second clutch C2 inserted between the output shaft and a gear connecting the output shaft to the ring gear of the first planetary gear mechanism. Continuously variable transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61136089A JPS62292956A (en) | 1986-06-13 | 1986-06-13 | Continuously variable device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61136089A JPS62292956A (en) | 1986-06-13 | 1986-06-13 | Continuously variable device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62292956A true JPS62292956A (en) | 1987-12-19 |
Family
ID=15166999
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61136089A Pending JPS62292956A (en) | 1986-06-13 | 1986-06-13 | Continuously variable device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62292956A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101761631A (en) * | 2008-12-12 | 2010-06-30 | 吴志强 | Compound rolling cone flat plate type stepless speed change concurrent starter |
-
1986
- 1986-06-13 JP JP61136089A patent/JPS62292956A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101761631A (en) * | 2008-12-12 | 2010-06-30 | 吴志强 | Compound rolling cone flat plate type stepless speed change concurrent starter |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7238135B2 (en) | Three-mode continuously variable transmission with a direct low mode and two split path high modes | |
| US4976670A (en) | Power transmission | |
| JP3921148B2 (en) | Power split type continuously variable transmission | |
| JP3954928B2 (en) | Vehicle power transmission device | |
| WO2001073319A1 (en) | Continuous variable transmission | |
| JPS6343620B2 (en) | ||
| JP3335179B2 (en) | Continuously variable transmission | |
| US5888161A (en) | All wheel drive continuously variable transmission having dual mode operation | |
| JPS61184270A (en) | Automatic transmission | |
| JPH09144835A (en) | Continuously variable transmission | |
| US5937711A (en) | All wheel drive continuously variable transmission having dual mode operation | |
| US5931760A (en) | Dual mode continuously variable transmission having multiple torque input paths | |
| US5961414A (en) | Dual mode continuously variable transmission having multiple torque input paths | |
| US5941789A (en) | All wheel drive continuously variable transmission having dual mode operation | |
| JPH04501163A (en) | Continuously variable transmission | |
| JPS62292956A (en) | Continuously variable device | |
| KR20210146471A (en) | Powertrain for electric vehicle | |
| JP3060769B2 (en) | Gearbox for automatic transmission | |
| JPS62118159A (en) | Power transmission speed change gear | |
| JPH0721947Y2 (en) | Belt type continuously variable transmission | |
| JPS6165963A (en) | Non-stage transmission | |
| JPS6338760A (en) | Continuous variable transmission | |
| KR20030017865A (en) | continuous variable transmission for use a vehicle | |
| KR200155306Y1 (en) | Idle gear | |
| JP3409046B2 (en) | Multi-stage transmission with differential gear |