JPS59117920A - Clutch for stepless speed change gear - Google Patents
Clutch for stepless speed change gearInfo
- Publication number
- JPS59117920A JPS59117920A JP57231099A JP23109982A JPS59117920A JP S59117920 A JPS59117920 A JP S59117920A JP 57231099 A JP57231099 A JP 57231099A JP 23109982 A JP23109982 A JP 23109982A JP S59117920 A JPS59117920 A JP S59117920A
- Authority
- JP
- Japan
- Prior art keywords
- rotating shaft
- clutch
- primary
- hydraulic pressure
- speed change
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、ベルト式無段変速機のクラッチに関し、特に
、機構が単純で部品が簡素化された小型化が容易なりラ
ッチに関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a clutch for a belt-type continuously variable transmission, and more particularly to a latch that has a simple mechanism, simplified parts, and is easily miniaturized.
相互間に■溝を形成して回転軸とともに回転する回転体
の一方が液圧シリンダによって軸方向に駆動されること
によりその■溝の溝幅が変更される変速プーリを、Ａ・
自互間隔が固定の互に平行な一次回転軸および２次回転
軸にそれぞれ設けるとともに、その変速プーリ間に伝導
ベルトが巻き掛けられてその１次回転軸と２次回転軸と
の回転速度比を無段階に変更し得る無段変速機において
、その１次回転軸とそれと同軸に設けられた駆動軸との
間に動力を伝達遮断するクラッチが知られてい−る。し
かしながら、斯る従来の無段変速機のクラツチは、クラ
ッチを操作するだめの独立の操作入力装置、シリンダ等
の出力装置、及びそれ等を連結する油圧回路等を必要と
するため、機構が複雑に在るとともに部品点数が多くな
シ、高価となり且つ容積が大きくなる不都合があった。A speed change pulley is a speed change pulley in which the groove width of the groove is changed by driving one of the rotating bodies that rotates together with the rotating shaft with a hydraulic cylinder in the axial direction by forming a groove between the two.
A primary rotating shaft and a secondary rotating shaft are provided parallel to each other with a fixed interval between each other, and a transmission belt is wound between the variable speed pulleys to adjust the rotational speed ratio between the primary rotating shaft and the secondary rotating shaft. 2. Description of the Related Art In a continuously variable transmission that can change the speed continuously, a clutch is known that transmits and disconnects power between its primary rotating shaft and a drive shaft coaxially provided therewith. However, the clutch of such a conventional continuously variable transmission requires an independent operation input device for operating the clutch, an output device such as a cylinder, and a hydraulic circuit that connects them, resulting in a complicated mechanism. However, there are disadvantages in that it requires a large number of parts, is expensive, and has a large volume.
また、クラッチの接続操作が急激に行われると、動力伝
達が瞬間的に行われて伝導ベルトと変速プーリとの間に
滑りが生じ、無段変速機の耐久性を低下させる一因とな
っていた。Additionally, if the clutch is engaged suddenly, the power is transmitted instantaneously, causing slippage between the transmission belt and the speed change pulley, which is one of the causes of reduced durability of the continuously variable transmission. Ta.
本発明は以上の事情を背景として為されたものであシ、
その目的とするところは、部品点数が少なく単純な機構
を備えしかも動力伝達が円滑に行われる無段変速機のク
ラッチを提供することにある。The present invention has been made against the background of the above circumstances.
The object is to provide a clutch for a continuously variable transmission that has a simple mechanism with a small number of parts and that can smoothly transmit power.
斯る目的を達成するため、本発明のクラッチは前記無段
変速機において、前記１次回転軸とその１次回転軸と同
軸に設けられた駆動軸との間に設けられてそれ等を断続
するクラッチであって、（１）前記１次回転軸及び駆動
軸のそれぞれに相対向した状態で設けられ、互に摺接可
能な摩擦部材（２）前記１次回転軸に軸方向移動可能に
設けられ前記液圧シリンダ内の液圧が高められて前記１
次回転軸変速プーリのＶ溝幅が小さくされるとぎ、その
液圧、またはその１次回転軸変速プーリの回転体の相互
に拡開しようとする反力を受けて前記Ｍ振部材の一方を
他方に押圧する押圧部材とを含むことを特徴とする。In order to achieve such an object, the clutch of the present invention is provided in the continuously variable transmission between the primary rotating shaft and a drive shaft provided coaxially with the primary rotating shaft, and connects and disconnects them. The clutch includes: (1) a friction member that is provided facing each of the primary rotation shaft and the drive shaft and that can slide into contact with each other; and (2) a friction member that is movable in the axial direction on the primary rotation shaft. and the hydraulic pressure in the hydraulic cylinder is increased to increase the hydraulic pressure in the hydraulic cylinder.
When the V-groove width of the next rotation shaft speed change pulley is made smaller, one of the M vibration members is It is characterized by including a pressing member that presses the other side.
この様にすれば、動力伝達開始時には一般に無段変速機
における変速比（回転速度比）が最も大ぎい状態である
ので、動力伝達開始に際して、１次回転体変速プーリの
溝幅を小さくするために液圧シリンダ内の液圧が高めら
れようとするとき、その液圧、またはその１次回転軸変
速プーリの回転体の相互に拡開しようとする反力を受け
て押圧部材が摩擦部材の一方を他方に押圧することによ
って、駆動軸と１次回転軸とが接続される。このため、
クラッチは上記液圧シリンダを作動させるだめの操作入
力装置及び油圧回路を用いて作動させられるので、クラ
ッチを独立に作動させるための油圧回路、操作入力装置
等を用いる場合に比較して、部品点数が少なく機構が簡
単となシフラッチ装置が小容積とされるとともに安価と
々るのである。In this way, since the gear ratio (rotational speed ratio) in the continuously variable transmission is generally at its maximum when power transmission starts, the groove width of the primary rotary speed change pulley can be made smaller when power transmission starts. When the hydraulic pressure in the hydraulic cylinder is about to increase, the pressing member is affected by the hydraulic pressure or the reaction force of the rotating bodies of the primary rotating shaft speed change pulley that try to expand each other. By pressing one against the other, the drive shaft and the primary rotation shaft are connected. For this reason,
Since the clutch is operated using the operation input device and hydraulic circuit that actuate the hydraulic cylinder, the number of parts is reduced compared to the case where a hydraulic circuit, operation input device, etc. are used to operate the clutch independently. The shift latch device, which has a simple mechanism with less noise, has a small volume and is inexpensive.
しかも、クラッチは可変プーリに掛けられた伝導ベルト
の側圧を高めると同時に接続されるので動力伝達が滑ら
かとなるとともにベルトと可変プーリとの滑りが解消さ
れ得て無段変速機の耐久性が向上させられるのである。Moreover, since the clutch is connected at the same time as increasing the lateral pressure of the transmission belt applied to the variable pulley, power transmission becomes smooth and slippage between the belt and the variable pulley can be eliminated, improving the durability of the continuously variable transmission. They are made to do so.
以下、本発明の一実施例を示す図面に基づいて詳細に説
明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described in detail below based on the drawings.
第１図において、変速機のハウジング１０内には自動車
のエンジンの出ツＪ軸に連結された駆動軸１２が支持さ
れているとともに、その駆動軸１２の外周に嵌装された
状態でスリーブ状の１次回転軸１４が回転可能に配設さ
れている。ハウジング１０内には、更に１次回転軸１４
と平行且つ相互間隔が固定に車輪等に回転力を伝達する
だめの２次回転軸１６が軸受１８によって回転可能に支
持されている。尚、２０はフライホイールである。In FIG. 1, a drive shaft 12 connected to an output J-shaft of an automobile engine is supported within a transmission housing 10, and a sleeve-like shape is fitted around the outer periphery of the drive shaft 12. A primary rotating shaft 14 is rotatably arranged. Inside the housing 10, there is further a primary rotating shaft 14.
A secondary rotation shaft 16 is rotatably supported by a bearing 18, parallel to and spaced apart from each other, for transmitting rotational force to wheels or the like. In addition, 20 is a flywheel.
１次回転軸１４及び２次回転軸１６には、それぞれの回
転軸に固定の固定回転体２２．２４と、軸方向に移動可
能に設けられ、固定回転体２２゜２４との間に伝導ベル
ト２６が掛けられるＶ溝を形成する可動回転体２８．８
０とから成る、溝幅な
の可変嬬可変ブー！１８２．３４がそれぞれ設けられて
いる。可変ブー リ３４の可動回転体３０は、２次回転
軸１６に固定の有底円筒状のシリンダ３６の外周に嵌合
され、２次回転軸１６に形成された通路３８を介してシ
リンダ３６内に液圧が供給されると、可動回転体３０が
ピストン作用を為して可変プーリ３４の■溝幅を小さく
する方向に移動させられるように方っている。The primary rotating shaft 14 and the secondary rotating shaft 16 are provided with fixed rotating bodies 22 and 24 fixed to the respective rotating shafts, and a transmission belt between the fixed rotating bodies 22 and 24, which are movable in the axial direction. A movable rotating body 28.8 forming a V groove in which 26 is hung.
The width of the groove is variable, consisting of 0! 182.34 are provided respectively. The movable rotating body 30 of the variable pulley 34 is fitted onto the outer periphery of a bottomed cylindrical cylinder 36 fixed to the secondary rotating shaft 16, and is inserted into the cylinder 36 through a passage 38 formed in the secondary rotating shaft 16. When hydraulic pressure is supplied to the movable rotary body 30, the movable rotating body 30 acts as a piston to move the variable pulley 34 in a direction that reduces the width of the groove.
一方、１次回転軸１４には開口部が可動回転体２８に対
向する有底円筒状のシリンダ部４０が形成されていると
ともに、可動回転体２８のシリンダ部４０側には軸方向
に突き出す円環状の突起４２が形成されている。そして
、その突起４２と１次回転軸１４との間には、軸方向に
摺動可能に断面り字形を成す円環状の第１ピストン４４
が摺動可能に嵌め入れられるとともに、その第１ピスト
ン４４の円筒部とシリンダ部４ｏとの間には、円環板状
の第２ピストン４６が軸方向の摺動可能に嵌め入れられ
、更にシリンダ部４ｏの底壁に形成された穴には小径の
第３ピストン４８が軸方向に摺動可能に嵌め入れられて
いる。従って、第１ビス１−７４４と可動回転体２８と
の間に形成された空間ａと第２ピストン４６とシリンダ
部４ｏ及び第３ピストン４８との間に形成された空間す
とに駆動軸Ｉ２に形成された通路５ｏ及び１次回転軸１
４に形成された通路５２を介して液圧が供給されると、
可動回転体２８は空間ａ内の液圧を受けるとともに空間
す内の液圧を受けた第２ピストン４６からの駆動力を受
けて、可変プーリ３２のＶ溝幅を小さくする方向に駆動
されるとともに、第３ピストン４８は可変プーリ３２が
ら離隔する方向に駆動されるようになって層る。すなわ
ち、シリンダ部４０、第２ピストン４６、第１ピストン
４４、突起４２は、液圧力を倍力して可動回転体２８を
付勢する液圧シリンダを構成しているのである。On the other hand, a bottomed cylindrical cylinder part 40 whose opening faces the movable rotary body 28 is formed in the primary rotating shaft 14, and a circular cylinder part 40 protruding in the axial direction is formed on the cylinder part 40 side of the movable rotary body 28. An annular projection 42 is formed. Between the protrusion 42 and the primary rotating shaft 14, there is provided an annular first piston 44 which is slidable in the axial direction and has a cross-sectional shape.
A second piston 46 having an annular plate shape is fitted between the cylindrical portion of the first piston 44 and the cylinder portion 4o so as to be slidable in the axial direction. A third piston 48 having a small diameter is fitted into a hole formed in the bottom wall of the cylinder portion 4o so as to be slidable in the axial direction. Therefore, the space a formed between the first screw 1-744 and the movable rotating body 28 and the space formed between the second piston 46, the cylinder part 4o and the third piston 48 are connected to the drive shaft I2. A passage 5o formed in and a primary rotating shaft 1
When hydraulic pressure is supplied through the passage 52 formed in 4,
The movable rotating body 28 is driven in the direction of reducing the V-groove width of the variable pulley 32 by receiving the hydraulic pressure in the space a and the driving force from the second piston 46 which has received the hydraulic pressure in the space. At the same time, the third piston 48 is driven in a direction away from the variable pulley 32. That is, the cylinder portion 40, the second piston 46, the first piston 44, and the protrusion 42 constitute a hydraulic cylinder that boosts the hydraulic pressure and urges the movable rotating body 28.
第３ピストン４８は、駆動軸１２ど１次回転軸１４との
間に設けられたクラッチ５４を作動させるものである。The third piston 48 operates a clutch 54 provided between the drive shaft 12 and the primary rotating shaft 14 .
すなわち、駆動軸Ｉ２に形成されたスプラインには、Ｈ
振部材である２枚の摩擦板５６が係合させられていると
ともに、シリンダ部４０からフライホイール２ｏ側に突
設された円環状の突起５８の内周面に形成された内周歯
には、摩擦板５６を挾む３枚の摩擦板６ｏが係合させら
れておシ、第３ピストン４８が液圧を受けてフライホイ
ール２０側に移動させられると、摩擦板６０と摩擦板５
６とが相互に押圧されて駆動軸１２の回転力が１次回転
軸１４に伝達されるようになっている。すなわち、クラ
ッチ５４は、摩擦板５６．６０と抑圧部材である第３ピ
ストン４８とから主として構成されているのである。尚
、６２は摩擦板６０のフライホイール２ｏ側への移動全
阻止するストッパである。That is, the spline formed on the drive shaft I2 has an H
Two friction plates 56, which are vibrating members, are engaged with each other, and inner peripheral teeth formed on the inner peripheral surface of an annular projection 58 protruding from the cylinder portion 40 toward the flywheel 2o side are engaged with each other. When the three friction plates 6o sandwiching the friction plate 56 are engaged and the third piston 48 is moved toward the flywheel 20 under hydraulic pressure, the friction plates 60 and 5
6 are pressed against each other so that the rotational force of the drive shaft 12 is transmitted to the primary rotation shaft 14. That is, the clutch 54 is mainly composed of friction plates 56, 60 and the third piston 48, which is a suppressing member. Note that 62 is a stopper that completely prevents the friction plate 60 from moving toward the flywheel 2o.
以下、本実施例の作動を説明する。The operation of this embodiment will be explained below.
動力伝達の開始時には、１次回転軸１４と２次回転軸１
６との変速比が最も大きい状態とされる必要があるので
、クラッチ５４の非接続時には空間ａ及び１〕に供給さ
れる液圧は略零に近い値とされるのに対し、シリンダ３
６内にはエンジンの回転数や変速比の変化に応じて高め
られる所定の液圧が供給される。このため、可変プーリ
３２のＶ溝幅は最も広くされるとともに、可変プーリ３
４のＶ溝幅は最も狭い状態とされる。第１図はこの状態
を示す。At the start of power transmission, the primary rotating shaft 14 and the secondary rotating shaft 1
Since the gear ratio between the cylinder 3 and the cylinder 3 needs to be the largest, when the clutch 54 is not engaged, the hydraulic pressure supplied to the spaces a and 1] is set to a value close to zero.
6 is supplied with a predetermined hydraulic pressure that is increased according to changes in engine speed and gear ratio. Therefore, the V groove width of the variable pulley 32 is made the widest, and the variable pulley 3
The V-groove width of No. 4 is the narrowest. FIG. 1 shows this situation.
次に、第２図の一点鎖線に示されるように、通路５０．
５２を介して空間ａ、ｂ内に供給される液圧が高められ
ると、第３ピストン４８が摩擦板５６、．６０を相互に
押圧するとともに、可動回転体２８が空間ａからの液圧
と第２ピストン４６からの力を受けて固定回転体２２側
に駆動され、伝導ベルト２６の側圧を高める。このとき
、クラッチ５４の作動荷重及び可変プーリ３２の作動荷
重は、第２図の実線及び破線に示されるように、空間ａ
及びｂへ供給される液圧の上昇に伴って上昇させられる
ので、駆動軸１２を介して伝達されるエンジンの出力は
円滑に１次回転軸１４及び２次回転軸１６に伝達される
。Next, as shown by the dashed line in FIG. 2, the passage 50.
52 into the spaces a, b, the third piston 48 moves against the friction plates 56, . 60 are pressed against each other, and the movable rotary body 28 is driven toward the fixed rotary body 22 by receiving the hydraulic pressure from the space a and the force from the second piston 46, thereby increasing the side pressure of the transmission belt 26. At this time, the operating load of the clutch 54 and the operating load of the variable pulley 32 are as shown in the solid line and broken line in FIG.
and b, so that the output of the engine transmitted via the drive shaft 12 is smoothly transmitted to the primary rotating shaft 14 and the secondary rotating shaft 16.
空間ａ及びｂに供給される液圧が更に高められるに伴っ
て可変プーリ３２の■溝幅が小さくされると、伝導ベル
ト２６の掛り径（有効径）が大ぎくされる一方、可変プ
ーリ３４においてはシリンダ３６内の液圧に抗して可動
回転体３０が移動させられて可変プーリ３４のＶ溝幅が
大きくされ、伝導ベルト２６の掛り径が小さくされる。When the groove width of the variable pulley 32 is reduced as the hydraulic pressure supplied to the spaces a and b is further increased, the hanging diameter (effective diameter) of the transmission belt 26 is greatly increased, while the variable pulley 34 is The movable rotating body 30 is moved against the hydraulic pressure in the cylinder 36, the V-groove width of the variable pulley 34 is increased, and the hanging diameter of the transmission belt 26 is decreased.
このため、無段変速機の変速比ｅが連続的に小さく変化
させられるのである。尚、第３図において可変プーリ３
２及び３４の作動荷重を液圧に置き換えだ値が実線及び
破線に示されているように、必要とされる作動変圧は変
速比Ｃおよび駆動軸１２に伝達される入力トルクＴｉｎ
の変化とともにも変化するが、空間ａ及びｂとシリ
ンダ３６内とに供給されるそれぞれの液圧は、その作動
液圧以上となるように予め設定されているのである。Therefore, the gear ratio e of the continuously variable transmission is continuously changed to a small value. In addition, in Fig. 3, the variable pulley 3
2 and 34 are replaced with hydraulic pressure. As shown by the solid and dashed lines, the required operating pressure is determined by the transmission ratio C and the input torque Tin transmitted to the drive shaft 12.
The hydraulic pressures supplied to the spaces a and b and the inside of the cylinder 36 are set in advance to be equal to or higher than the working hydraulic pressure, although the hydraulic pressures are set in advance to be equal to or higher than the working hydraulic pressure.
この様に本実施例によれば、クラッチ５４は無段変速機
の変速比を変化させるための液圧に基づいて第３ピスト
ン４８が摩擦板５６．６０を押圧することにより ＩＩ
続作動させられるので、クラッチを独立の入力操作装置
、シリンダ等の出力装置それ等を接続する油圧回路を用
いる場合に比較して、クラッチ操作機構が大幅に簡素化
されて部品点数が少なく々す、クラッチ装置及びこれが
設けられる無段変速機の容積及び価格が効果的に低減さ
れるのである。As described above, according to this embodiment, the clutch 54 is operated by the third piston 48 pressing the friction plate 56.60 based on the hydraulic pressure for changing the gear ratio of the continuously variable transmission.
Since the clutch can be operated continuously, the clutch operating mechanism is greatly simplified and has fewer parts compared to using a hydraulic circuit that connects the clutch to an independent input operating device, output device such as a cylinder, etc. Therefore, the volume and cost of the clutch device and the continuously variable transmission in which it is installed are effectively reduced.
しかも、クラッチを独立に操作する場合に比較して、ク
ラッチの伝達トルりの増加とともに可変プーリ３２に掛
けられた伝導ベルト２６の側圧が増加させられるので、
エンジンの回転力の伝達が極めて円滑となるとともに、
伝導ベルト２６と可変プーリ３２との間の滑しが解消さ
れて耐久性が好適に向上させられるのである。Furthermore, compared to the case where the clutches are operated independently, the lateral pressure of the transmission belt 26 applied to the variable pulley 32 is increased as the transmission torque of the clutch increases.
The transmission of engine torque becomes extremely smooth, and
Slippage between the transmission belt 26 and the variable pulley 32 is eliminated, and durability is suitably improved.
次に、本発明の他の実施例を説明する。尚、以下の説明
において前述の実施例と共通する部分には同一の符号を
伺して説明を省略する。Next, another embodiment of the present invention will be described. In the following explanation, the same reference numerals will be used for the same parts as in the above-mentioned embodiment, and the explanation will be omitted.
第４図において、シリンダ部４０の摩擦板６０側には空
間すと連通ずる大径のシリンダボア７２が形成されてお
シ、そのシリンダボア７２には第４ピストン７４が摺動
可能に嵌め込まれている。In FIG. 4, a large diameter cylinder bore 72 is formed on the friction plate 60 side of the cylinder portion 40 and communicates with the space, and a fourth piston 74 is slidably fitted into the cylinder bore 72. .
また、摩擦板５６及び６０はそれぞれ大径とされ摩擦面
積が拡大されている。本実施例によれば、クラッチ５４
の作動荷重が低くされるとともにその伝達トルりが大き
くされる利点がある。Further, each of the friction plates 56 and 60 has a large diameter to increase the friction area. According to this embodiment, the clutch 54
This has the advantage of lowering the operating load and increasing the transmitted torque.
第５図において、１次回転軸１４には１次回転軸１４と
ともに回転するが軸方向に移動可能な一対の可動回転体
７６．７８が設けられてしる。これ等回転体７６．７８
の間には伝導ベルト２６が掛けられる■溝が形成され、
回転体７６．７８が可変プーリ３２を形成している。回
転体７６は１次回転軸１４に固定のシリンダ８０の外周
に嵌合されておシ、シリンダ８０内に駆動軸１２に形成
された通路８２及び１次回転軸１４に形成された通路８
４を介して液圧が供給されると、可動回転体７６が可動
回転体７８に向って移動させられ、■溝幅が狭くされる
ようになっている。１次回転軸１４に固定された有底円
筒状の摩擦板保持部８６の内周面に形成された保合歯と
、駆動軸１２の外周面に形成されたスプラインとには、
Ｍ振板６０及び５６が保合させられており、摩擦板保持
部８６に形成された穴に摺動可能に嵌合された抑圧部材
８８が、摩擦板６０と可動回転体７８との間に挾捷れて
いる。In FIG. 5, the primary rotating shaft 14 is provided with a pair of movable rotating bodies 76, 78 that rotate together with the primary rotating shaft 14 but are movable in the axial direction. These rotating bodies 76.78
A groove is formed between the two, into which the conductive belt 26 is hung.
The rotating bodies 76, 78 form the variable pulley 32. The rotating body 76 is fitted around the outer periphery of a cylinder 80 fixed to the primary rotating shaft 14 , and has a passage 82 formed in the drive shaft 12 and a passage 8 formed in the primary rotating shaft 14 in the cylinder 80 .
When hydraulic pressure is supplied through 4, the movable rotating body 76 is moved toward the movable rotating body 78, and the groove width is narrowed. Retaining teeth formed on the inner circumferential surface of the bottomed cylindrical friction plate holding portion 86 fixed to the primary rotating shaft 14 and splines formed on the outer circumferential surface of the drive shaft 12 include:
The M diaphragms 60 and 56 are held together, and a suppressing member 88 slidably fitted into a hole formed in the friction plate holding portion 86 is located between the friction plate 60 and the movable rotating body 78. It's torn.
従って、図示し々い２次回転軸に設けられた可変グーり
の溝幅を変化させるシリンダ内にトルク伝達のために液
圧が供給されるに伴って、伝導ベルト２６に張力が発生
し、この伝導ベルト２６を挟圧する反力に従って可動回
転体７８が受ける反力が抑圧部材８８を介して摩擦板６
０に向って伝達される。す々わち、抑圧部材８８は可動
回転体７８が受ける反力を受けて摩擦板５Ｇ及び６０を
相互に押圧し、駆動軸１２の回転力を１次回転軸１４及
び伝導ベアＬ／ ｌ−２６を介し７て２次回転軸１６に
伝達するのである。Therefore, as hydraulic pressure is supplied for torque transmission into the cylinder that changes the groove width of the variable groove provided on the secondary rotating shaft (not shown), tension is generated in the transmission belt 26. The reaction force that the movable rotating body 78 receives in accordance with the reaction force that pinches the conduction belt 26 is transmitted to the friction plate 6 via the suppressing member 88.
transmitted towards 0. In other words, the suppressing member 88 presses the friction plates 5G and 60 against each other in response to the reaction force received by the movable rotating body 78, and transfers the rotational force of the drive shaft 12 to the primary rotating shaft 14 and the transmission bear L/l-. It is transmitted to the secondary rotating shaft 16 via 26 and 7.
尚、北述したのはあく寸でも本発明の一実施例であり、
本発明はその精神を逸脱しない範囲において種々変更さ
れ得るものである。It should be noted that what has been described above is just one embodiment of the present invention,
The present invention can be modified in various ways without departing from its spirit.
第１図は本発明の一実施例を含む無段変速機の要部を示
す断面図である。第２図及び第３図は、第１図の実施例
の作動を説明するための、供給圧力及び作動荷重の時間
変化、及び作動液圧と変速比との関係をそれぞれ示す図
表である。第４図及び第５図は、それぞれ本発明の他の
実施例の要部を示す断面図である。
１２：駆動軸 １４：１次回転軸１６：２次
回転軸 ２２，２４：固定回転体２８．３０，７
６．７８：可動回転体
２６：伝導ベルト ８２，３４：変速プーリ３６
．８０ニジリンダ（液圧シリンダ）４８：第３ピストン
（抑圧部材）
５４：クラッチ
５６．６０：摩擦板（摩擦部材）
８８：押圧部材FIG. 1 is a sectional view showing essential parts of a continuously variable transmission including an embodiment of the present invention. 2 and 3 are charts showing temporal changes in supply pressure and operating load, and the relationship between operating fluid pressure and gear ratio, respectively, to explain the operation of the embodiment shown in FIG. 1. FIGS. 4 and 5 are sectional views showing essential parts of other embodiments of the present invention, respectively. 12: Drive shaft 14: Primary rotation axis 16: Secondary rotation axis 22, 24: Fixed rotation body 28. 30, 7
6.78: Movable rotating body 26: Transmission belt 82, 34: Speed change pulley 36
．． 80 Niji cylinder (hydraulic cylinder) 48: Third piston (suppressing member) 54: Clutch 56.60: Friction plate (friction member) 88: Pressing member
Claims (1)
の一方が液圧シリンダによって軸方向に駆動されること
によシ該■溝の溝幅が変更される変速プーリを、相互間
隔が固定の互に平行々−一次回転軸よび２次回転軸にそ
れぞれ設けるとともに、該変速プーリ間に伝導ベルトが
巻きかけられて該１次回転軸と２次回転軸との回転速度
比を無段階に変更し得る無段変速機において、前記１次
回転軸と該１次回転軸と同軸と設けられた駆動軸との間
に設けられてそれ等を断続するクラッチであって、 前記１次回転軸および駆動軸のそれぞれに相列向した状
態で設けられ、互に摺接可能な摩擦部材と、 前記１次回転軸に軸方向移動可能に設けられ、前記液圧
シリンダ内の液圧が高められて前記１次回転軸変速プー
リの■溝幅が小さくされるとぎ、該液圧、まだは該１次
回転軸変速プーリの回転体の相互に拡開しようとする反
力を受けて前記摩擦部材の一方を他方に押圧する抑圧部
材とを含むことを特徴とする無段変速機のクラッチ。[Claims] A speed change in which the groove width of the groove is changed by driving one of the rotating bodies that rotate together with the rotating shaft with a V vortex between them in the axial direction by a hydraulic cylinder. Pulleys are provided parallel to each other at fixed intervals on the primary rotating shaft and the secondary rotating shaft, and a transmission belt is wound between the variable speed pulleys to connect the primary rotating shaft and the secondary rotating shaft. In a continuously variable transmission capable of steplessly changing a rotational speed ratio, a clutch is provided between the primary rotating shaft and a drive shaft provided coaxially with the primary rotating shaft to connect and disconnect them. a friction member that is provided on each of the primary rotation shaft and the drive shaft so as to be in mutual sliding contact with each other; When the groove width of the primary rotating shaft speed change pulley is reduced by increasing the hydraulic pressure within the groove, the hydraulic pressure still causes the rotational bodies of the primary rotating shaft speed change pulley to spread out against each other. A clutch for a continuously variable transmission, comprising a suppressing member that presses one of the friction members against the other in response to a force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57231099A JPS59117920A (en) | 1982-12-24 | 1982-12-24 | Clutch for stepless speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57231099A JPS59117920A (en) | 1982-12-24 | 1982-12-24 | Clutch for stepless speed change gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS59117920A true JPS59117920A (en) | 1984-07-07 |
Family
ID=16918275
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57231099A Pending JPS59117920A (en) | 1982-12-24 | 1982-12-24 | Clutch for stepless speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59117920A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61157834A (en) * | 1984-12-24 | 1986-07-17 | ボーグ・ワーナー・コーポレーシヨン | Starting clutch |
-
1982
- 1982-12-24 JP JP57231099A patent/JPS59117920A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61157834A (en) * | 1984-12-24 | 1986-07-17 | ボーグ・ワーナー・コーポレーシヨン | Starting clutch |
| JPH026925B2 (en) * | 1984-12-24 | 1990-02-14 | Borg Warner |
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