JPH0337655B2 - - Google Patents
Info
- Publication number
- JPH0337655B2 JPH0337655B2 JP55110041A JP11004180A JPH0337655B2 JP H0337655 B2 JPH0337655 B2 JP H0337655B2 JP 55110041 A JP55110041 A JP 55110041A JP 11004180 A JP11004180 A JP 11004180A JP H0337655 B2 JPH0337655 B2 JP H0337655B2
- Authority
- JP
- Japan
- Prior art keywords
- clutch
- spring
- movable member
- cam
- driven shaft
- 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 - Lifetime
Links
- 230000005540 biological transmission Effects 0.000 description 14
- 238000007689 inspection Methods 0.000 description 5
- 230000001133 acceleration Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
Landscapes
- Mechanical Operated Clutches (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Description
【発明の詳細な説明】
(産業上の利用分野)
本発明は自動二輪車等の動力伝達、変速装置に
介設されるクラツチ装置の改良に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an improvement in a clutch device installed in a power transmission and transmission device of a motorcycle or the like.
(従来の技術)
駆動軸と被動軸との間に設けられ、駆動軸、被
動軸間の動力伝達の断接を行うクラツチ装置はよ
く知られている。(Prior Art) A clutch device that is provided between a drive shaft and a driven shaft and connects and disconnects power transmission between the drive shaft and the driven shaft is well known.
この種のクラツチ装置は、クランクシヤフト、
或はこれから導出された駆動軸で駆動されるドラ
ム状のクラツチアウタと、被動軸に繋るドラム状
のクラツチインナと、この間に介設され、上記ア
ウタ、インナの夫々に軸方向摺動可能に係止され
た複数のクラツチデイスク、クラツチプレート
と、これらを摩擦係合方向に弾圧するクラツチ断
接用バネとから成り、クラツチの断接は、クラツ
チバネで弾圧されるクラツチプレツシヤプレート
をクラツチレバー等による操作で軸方向に拘束
し、クラツチバネの伸長状態で摩擦係合を開離
し、クラツチを断絶し、クラツチバネの伸長方向
への拘束の解除で上記クラツチプレツシヤプレー
トを弾圧し、摩擦係合を復帰し、クラツチを接合
する。 This type of clutch device is used for crankshaft,
Alternatively, a drum-shaped clutch outer driven by a drive shaft derived from this, a drum-shaped clutch inner connected to a driven shaft, and interposed between the clutch outer and the clutch inner, and locked to each of the outer and inner so as to be slidable in the axial direction. It consists of a plurality of clutch disks and plates, and a spring for clutch engagement/disengagement that presses these in the direction of frictional engagement.The clutch is engaged/disconnected by using a clutch lever or the like to move the clutch pressure plate, which is compressed by the clutch springs. The clutch is restrained in the axial direction by operation, and the frictional engagement is released when the clutch spring is stretched, disconnecting the clutch. When the clutch spring is released from restraint in the stretching direction, the clutch pressure plate is pressed, and the frictional engagement is restored. and connect the clutch.
(発明が解決しようとする課題)
従来のこの種のクラツチは、クラツチプレツシ
ヤプレートを介して摩擦係合せしめるクラツチデ
イスク、クラツチプレートの摩擦係合弾圧力を専
らクラツチバネ固有の弾発力に依存している。た
めに係合の確実を期するためクラツチバネのバネ
荷重は必要な値に定められ、大型、大排気量、大
馬力のものではバネ荷重も高いものが要求され
る。従つてクラツチの摩擦係合状態からの断絶操
作即ちクラツチの開操作は上記の大きなバネ荷重
に抗して行わなければならず、大きな操作荷重を
必要とし、操作がしにくい。又クラツチの接合状
態の弾圧力は一定で、ために減速時等に被動軸か
ら大きなバツクロードが働いた場合、これのトル
クをクラツチ装置に伝えてしまい、伝動系や変速
系にこれが伝わり、伝動系や変速系に悪影響を及
ぼし、これらの耐久性を低下させたりする虞れが
あり、ために伝動系、変速系はバツクロードを考
慮して必要以上の強度を付与するように設計しな
ければならない。(Problems to be Solved by the Invention) Conventional clutches of this kind rely exclusively on the elastic force inherent in the clutch spring for the frictional engagement elastic force of the clutch disk and clutch plate, which are frictionally engaged via the clutch pressure plate. are doing. Therefore, in order to ensure reliable engagement, the spring load of the clutch spring is set to a necessary value, and large-sized, large-displacement, and high-horsepower engines require a high spring load. Therefore, the operation of disengaging the clutch from the frictional engagement state, that is, the operation of opening the clutch, must be performed against the above-mentioned large spring load, which requires a large operating load and is difficult to operate. In addition, the elastic force of the clutch in its engaged state is constant, so if a large backload is applied from the driven shaft during deceleration, the torque will be transmitted to the clutch device, which will be transmitted to the transmission system and transmission system, causing damage to the transmission system. There is a risk that the transmission system and transmission system may be adversely affected and their durability may be reduced, so the transmission system and transmission system must be designed to have more strength than necessary in consideration of the back load.
本発明者は従来のクラツチ装置における上記不
都合を改善すべく本発明をなしたもので、本発明
の目的とする処は、上記クラツチバネを加速時に
は圧縮する方向に、即ちバネ荷重を高めて摩擦係
合を確実に行う方向に調整し、減速時や静止運転
時にはクラツチバネを伸長する方向、即ちバネ荷
重を低下させて摩擦係合を弱め、或は開離する方
向に調整するようにしたカム機構等からなる調整
機構を付設するようにしたクラツチ装置を得せし
めるにある。 The present inventor has devised the present invention in order to improve the above-mentioned disadvantages in conventional clutch devices.The object of the present invention is to compress the clutch spring during acceleration, that is, increase the spring load to reduce friction. A cam mechanism, etc. that is adjusted in the direction to ensure that the clutch spring is engaged securely, and in the direction that the clutch spring is extended during deceleration or stationary operation, that is, the spring load is lowered to weaken the frictional engagement, or the clutch spring is disengaged. The present invention provides a clutch device which is provided with an adjustment mechanism consisting of the following.
(課題を解決するための手段)
前記課題を解決するため本発明は歯車列を介し
て駆動軸側に連結されるクラツチアウタと、該ク
ラツチアウタ内に配置され、前記クラツチアウタ
に対して摺動自在なクラツチインナと、該クラツ
チインナと前記クラツチアウタとの間に設けられ
るクラツチデイスク及びクラツチプレートと、前
記クラツチインナの端部に一体的に形成され、前
記クラツチデイスク及びクラツチプレートの一端
側に位置するプレツシヤプレートと、クラツチデ
イスク及びクラツチプレートの他端側に位置する
クラツチセンタと、前記被動軸に固定される固定
部材と、前記クラツチインナに取り付けられ、前
記固定部材に対して被動軸の軸回り方向に回動可
能且つ軸線方向に摺動可能な可動部材と、該可動
部材と前記クラツチインナとの間に設けられ、前
記クラツチインナ及びプレツシヤプレートを前記
クラツチデイスクとクラツチプレートの摩擦係合
方向に弾圧するとともに前記可動部材を固定部材
側に弾圧するクラツチバネとから成り、前記固定
部材に凹カムを形成するとともに前記可動部材に
前記凹カムに係合する凸カムを形成し、前記凹カ
ムの深さを、駆動軸からの駆動による可動部材の
回転方向に漸次浅く形成し、前記クラツチバネを
前記クラツチインナの凹部空間内に配置したこと
を特徴とする。(Means for Solving the Problems) In order to solve the above problems, the present invention provides a clutch outer that is connected to the drive shaft side via a gear train, and a clutch inner that is disposed within the clutch outer and is slidable with respect to the clutch outer. a clutch disk and a clutch plate provided between the clutch inner and the clutch outer; a pressure plate integrally formed at an end of the clutch inner and located on one end side of the clutch disk and clutch plate; a clutch center located on the other end side of the clutch disk and the clutch plate; a fixing member fixed to the driven shaft; and a clutch center attached to the clutch inner and rotatable in a direction around the axis of the driven shaft with respect to the fixing member. a movable member that is slidable in the axial direction; and a movable member that is provided between the movable member and the clutch inner and presses the clutch inner and the pressure plate in the direction of frictional engagement between the clutch disk and the clutch plate. a clutch spring that presses the concave cam toward the fixed member, a concave cam is formed on the fixed member, a convex cam that engages with the concave cam is formed on the movable member, and the depth of the concave cam is adjusted from the drive shaft. The clutch spring is formed to be gradually shallower in the direction of rotation of the movable member driven by the clutch inner, and the clutch spring is disposed within the recess space of the clutch inner.
(作 用)
加速時等駆動軸からの駆動時に凹カムと凸カム
の係合を浅くしてクラツチバネを圧縮させるので
ばね荷重が高まり、クラツチバネのセツト荷重が
低くても、係合を強固、確実に行ない、動力ロス
をなくすことができる。又減速時等被動軸からの
駆動時には凹カムと凸カムの係合を深くしてクラ
ツチバネを伸長させバツクロードを抑制し、伝動
系の耐久性を向上させることができる。(Function) When driving from the drive shaft, such as during acceleration, the engagement between the concave and convex cams is shallowed and the clutch spring is compressed, increasing the spring load, making the engagement strong and reliable even when the set load of the clutch spring is low. can be carried out to eliminate power loss. Furthermore, when driving from the driven shaft, such as during deceleration, the engagement between the concave cam and the convex cam is deepened to extend the clutch spring, suppressing back load and improving the durability of the transmission system.
(実施例)
次に本発明の好適一実施例を添付図面に従つて
詳述する。(Embodiment) Next, a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.
第1図は本発明にかかるクラツチ装置の縦断側
面図を、第2図は主要部分の分解斜視図を、第3
図及び第4図は作用説明図を示す。 Fig. 1 is a vertical sectional side view of the clutch device according to the present invention, Fig. 2 is an exploded perspective view of the main parts, and Fig. 3 is an exploded perspective view of the main parts.
4 and 4 show action explanatory diagrams.
第1図において1はクランク軸、或はクランク
軸で駆動される駆動軸で、2はこれと平行する被
動軸である。駆動軸1にはギヤ3が固設され、ギ
ヤ3は被動軸2上に回転自在に嵌合されたクラツ
チアウタ4の基部に付設されたギヤ5と噛合して
いる。クラツチアウタ4の先部には大径のドラム
部4aが形成され、この内径部に放射状に設けた
溝4b…に複数のクラツチデイスク6…の外周基
部6aが軸方向摺動可能に係止されている。 In FIG. 1, 1 is a crankshaft or a drive shaft driven by the crankshaft, and 2 is a driven shaft parallel to this. A gear 3 is fixed to the drive shaft 1, and the gear 3 meshes with a gear 5 attached to the base of a clutch outer 4 rotatably fitted onto the driven shaft 2. A large-diameter drum portion 4a is formed at the tip of the clutch outer 4, and outer peripheral base portions 6a of a plurality of clutch disks 6 are locked in grooves 4b radially provided in the inner diameter portion of the drum portion 4a so as to be slidable in the axial direction. There is.
クラツチアウタ4のドラム部4aの内径部内に
は端部にプレツシヤプレート7を形成したクラツ
チインナ7aを配設し、このクラツチインナ7a
の外径部には溝7b…が放射状に形成され、これ
に複数のクラツチプレート8…が内径側の基部8
aで軸方向摺動可能に係止され、該プレート8…
は上記のクラツチデイスク6…の間に交互に配設
され、夫々8…,6…は径方向の大部分が径方向
においてラツプする。 A clutch inner 7a having a pressure plate 7 formed at its end is disposed within the inner diameter of the drum portion 4a of the clutch outer 4.
Grooves 7b... are formed radially on the outer diameter part of the grooves 7b, and a plurality of clutch plates 8... are formed in the base part 8 on the inner diameter side.
The plates 8...
are arranged alternately between the clutch disks 6, and most of the radial portions of the clutch discs 8, 6, and so on overlap in the radial direction.
クラツチインナ7aの内径部には軸方向溝より
なるスプライン7cを形成し、これに内径側に配
した可動部材9の外径ドラム部9a外周に形成し
たスプライン9bを係合し、可動部材9はスプラ
イン7c,9bにより軸方向に摺動可能とする。
この可動部材9のリング状円板部9cの外壁とク
ラツチインナ7aの先部内径部に部分的に内径方
向に突設したバネ受部7d間にクラツチバネ10
を縮装し、バネ10はバネ受部7dに軸方向に突
設したガイド7eでガイドされる。 A spline 7c consisting of an axial groove is formed on the inner diameter part of the clutch inner 7a, and a spline 9b formed on the outer periphery of the outer diameter drum part 9a of the movable member 9 disposed on the inner diameter side is engaged with the spline 7c. 7c and 9b enable sliding in the axial direction.
A clutch spring 10 is held between the outer wall of the ring-shaped disk portion 9c of the movable member 9 and the spring receiving portion 7d partially protruding in the inner diameter direction at the tip end of the clutch inner 7a.
The spring 10 is guided by a guide 7e that projects from the spring receiving portion 7d in the axial direction.
被動軸2の先部には固定部材11の筒状基部1
1aを嵌合固定し、これの後端フランジ部11b
外径部11cを可動部材9の外径部後端に設けた
リング状フランジ部9dで拘束せしめ、フランジ
部11bの外径側周辺部の前壁11dを円板部9
cの内側後壁9eに当接せしめる。固定部材11
の基部11a上にはクラツチセンタ12の基部1
2aを嵌着し、これの外径先部12bを最先端の
クラツチプレート6aに対峙せしめ、プレツシヤ
プレート7に働く弾圧力を支持する如くし、セン
タ12の先部12b内径部に形成した溝12cが
クラツチインナ7a外径の溝7b先端部と係合し
ている。尚図面中13は可動部材9の係止用クリ
ツプを、14はプレツシヤプレート7を操作レバ
ー15で開離方向に操作する駒を示す、操作レバ
ー15はアーム16のロツドによる回動で操作さ
れる。前記操作レバー15の中間部分には支持部
材15aを固設し、この支持部材15a及び操作
レバー15に形成した取付孔15bに調整ねじ1
5cを螺合する。又、クラツチ装置を覆うカバー
cには点検窓c1を形成し、この点検窓c1には
蓋体c2に脱着自在に取付ける。前記調整ねじ1
5cはケースc内で前記点検窓c1に臨み、且つ
被動軸2の中心線上に位置する。前記調整ねじは
クラツチの作動時期を調整するものであり、この
調整は蓋体c2を外して調整ねじc2をドライバ
ー等で回動させ、進退動させることで行う。 A cylindrical base 1 of a fixing member 11 is provided at the tip of the driven shaft 2.
1a is fitted and fixed, and the rear end flange portion 11b of this
The outer diameter portion 11c is restrained by a ring-shaped flange portion 9d provided at the rear end of the outer diameter portion of the movable member 9, and the front wall 11d of the outer diameter side peripheral portion of the flange portion 11b is fixed to the disk portion 9.
abut against the inner rear wall 9e of c. Fixed member 11
The base 11a of the clutch center 12 is mounted on the base 11a of the clutch center 12.
2a is fitted, and its outer diameter tip 12b is opposed to the most advanced clutch plate 6a, so as to support the elastic force acting on the pressure plate 7. The groove 12c engages with the tip of the groove 7b on the outer diameter of the clutch inner 7a. In the drawings, reference numeral 13 indicates a clip for locking the movable member 9, and reference numeral 14 indicates a piece for operating the pressure plate 7 in the opening direction with an operating lever 15. The operating lever 15 is operated by rotating the arm 16 with a rod. be done. A support member 15a is fixed to the middle part of the operating lever 15, and an adjustment screw 1 is inserted into the mounting hole 15b formed in the support member 15a and the operating lever 15.
Screw together 5c. In addition, an inspection window c1 is formed in the cover c covering the clutch device, and a cover c2 is detachably attached to the inspection window c1. Said adjustment screw 1
5c faces the inspection window c1 inside the case c and is located on the center line of the driven shaft 2. The adjustment screw is used to adjust the actuation timing of the clutch, and this adjustment is performed by removing the cover c2 and rotating the adjustment screw c2 with a screwdriver or the like to move it forward or backward.
ところで固定部材11のフランジ部11bの外
壁部には第2図、第3図及び第4図で示される如
く軸方向への深さが異なり、軸方向への傾斜面1
7aを有する凹カム17が形成される。一方、可
動カム9の円板部9cの内側後壁9eには軸方向
への凸カム18が凹カム17と係合する如く突設
され、凸カム18の先端には上記傾斜面17aと
対応する傾斜面18aを備える。凸カム18の円
周方向の幅は凹カム17より充分に小さい。 By the way, as shown in FIGS. 2, 3, and 4, the outer wall of the flange portion 11b of the fixing member 11 has different depths in the axial direction, and has an inclined surface 1 in the axial direction.
A concave cam 17 having a diameter 7a is formed. On the other hand, an axially protruding convex cam 18 is provided on the inner rear wall 9e of the disk portion 9c of the movable cam 9 so as to engage with the concave cam 17, and the tip of the convex cam 18 corresponds to the inclined surface 17a. It has an inclined surface 18a. The width of the convex cam 18 in the circumferential direction is sufficiently smaller than that of the concave cam 17.
次にその作用、効果を説明すると、エンジンの
出力は駆動軸1、ギヤ3,5、クラツチアウタ
4、クラツチデイスク6、プレート8、センタ1
2、プレツシヤプレート7及びクラツチインナ7
a、可動部材9、固定部材11を介して被動軸2
に伝達される。 Next, to explain its function and effect, the output of the engine is generated by the drive shaft 1, gears 3 and 5, clutch outer 4, clutch disc 6, plate 8, center 1.
2. Pressure plate 7 and clutch inner 7
a, driven shaft 2 via movable member 9 and fixed member 11
transmitted to.
第3図はニユートラル状態或は減速時の状態
で、凸カム18は凹カム17の最も深い位置に係
合し、従つてバネ10のセツト長さlは長く伸長
状態にある。従つてプレツシヤプレート7に作用
するバネ荷重は小さく、摩擦係合力は弱い。この
ためコマ14を介してプレツシヤプレート7を第
1図中左方に移動して係合を解除する操作は、少
ない操作荷重で行えることとなり、操作は容易と
なる。 FIG. 3 shows a neutral state or a state during deceleration, in which the convex cam 18 is engaged with the deepest position of the concave cam 17, so that the set length l of the spring 10 is long and in an extended state. Therefore, the spring load acting on the pressure plate 7 is small, and the frictional engagement force is weak. Therefore, the operation of moving the pressure plate 7 to the left in FIG. 1 via the top 14 to release the engagement can be performed with a small operating load, making the operation easy.
クラツチ接合状態で発進させ、加速時即ち、駆
動軸側からの駆動時においては、駆動側である可
動部材9が被動軸側の被動の固定部材11に対し
て先行し、円周方向に回転位相差が生じ、この結
果傾斜面18a,17aに案内されて凸カム17
は軸方向に移動する。これによりバネ10は圧縮
されて第4図に示される如くそのセツト長さはl1
と短くなり、即ちバネ10は圧縮されてバネの一
端を受けるプレツシヤプレート7に働くバネ荷重
は高まり、摩擦係合を強固にし、動力ロスを少な
くする。 When the clutch is engaged and the vehicle is started, during acceleration, that is, when driving from the drive shaft side, the movable member 9 on the drive side precedes the driven fixed member 11 on the driven shaft side, and the rotational position in the circumferential direction increases. A phase difference occurs, and as a result, the convex cam 17 is guided by the inclined surfaces 18a and 17a.
moves in the axial direction. As a result, the spring 10 is compressed and its set length is l 1 as shown in FIG.
In other words, the spring 10 is compressed, and the spring load acting on the pressure plate 7 that receives one end of the spring increases, thereby strengthening the frictional engagement and reducing power loss.
減速時、即ち被動軸側からの駆動時には可動部
材9に対して固定部材11側が先行し、前述とは
逆方向に回転位相差を生じ、凸カム18は傾斜面
17a,18aを介して相対的に凹カム17の深
い方向に移動して第3図の如くバネ10の軸方向
長さは伸長し、この結果プレツシヤプレート7に
働くバネ荷重は低くなり、摩擦係合弾圧力は弱く
なる。従つて駆動輪、被動軸を介して伝動系等に
伝達される過大なバツクロードは上記摩擦係合弾
圧力の低下で吸収され、伝動系等への過大なバツ
クロードの作用を緩和し、これを保護することと
なる。そして停止時にはバネ荷重によつて第3図
の状態に復する。 During deceleration, that is, when driving from the driven shaft side, the fixed member 11 side precedes the movable member 9, creating a rotational phase difference in the opposite direction to the above, and the convex cam 18 is moved relative to the movable member 9 through the inclined surfaces 17a and 18a. As the concave cam 17 moves deeper, the axial length of the spring 10 increases as shown in FIG. 3, and as a result, the spring load acting on the pressure plate 7 becomes lower, and the frictional engagement elastic force becomes weaker. . Therefore, excessive backload transmitted to the transmission system, etc. via the driving wheels and driven shaft is absorbed by the reduction in the frictional engagement elastic pressure, which alleviates the effect of excessive backload on the transmission system, etc., and protects it. I will do it. When stopped, the state shown in FIG. 3 is restored by the spring load.
以上図示実施例ではカムを凹凸カムとしたが、
具体的には上記に限られず任意である。 In the embodiment shown above, the cam is a concave-convex cam, but
Specifically, it is not limited to the above, but is arbitrary.
ところで本実施例では調整ねじ15cをケース
c内に配置したので従来のようにケースcに調整
ねじ取付用の孔を形成する必要がなくなり、調整
ねじ15cの調整時等にケースc内のオイルが外
部に漏れるのを防止することができる。又、点検
窓c1の蓋体c2を取外せばケースc内の調整ね
じ15cを目視できるので調整が容易である。 By the way, in this embodiment, since the adjusting screw 15c is arranged inside the case c, there is no need to form a hole for installing the adjusting screw in the case c as in the conventional case, and the oil inside the case c is removed when adjusting the adjusting screw 15c. It can prevent leakage to the outside. Furthermore, by removing the lid c2 of the inspection window c1, the adjustment screw 15c inside the case c can be visually checked, making adjustment easy.
(発明の効果)
以上述べたように本発明によれば加速時等駆動
軸からの駆動時に凹カムと凸カムの係合を浅くし
てクラツチバネを圧縮させるのでバネ荷重が高ま
り、クラツチバネのセツト荷重が低くても、係合
を強固、確実に行ない、動力ロスをなくすことが
できる。又減速時等被動軸からの駆動時には凹カ
ムと凸カムの係合を深くしてクラツチバネを伸長
させバツクロードを抑制し、伝動系の耐久性を向
上させることができる。又本発明ではクラツチバ
ネがカム作動用バネを兼ねているため、バネは1
つですみ、クラツチ装置の部品点数、制作工程の
減少を図れ、又クラツチ装置の小型化、重量の低
減化を図ることができる。(Effects of the Invention) As described above, according to the present invention, when driving from the drive shaft such as during acceleration, the engagement between the concave cam and the convex cam is made shallow and the clutch spring is compressed, thereby increasing the spring load and reducing the set load of the clutch spring. Even if the power is low, engagement can be performed firmly and reliably, and power loss can be eliminated. Furthermore, when driving from the driven shaft, such as during deceleration, the engagement between the concave cam and the convex cam is deepened to extend the clutch spring, suppressing back load and improving the durability of the transmission system. In addition, in the present invention, since the clutch spring also serves as a cam actuation spring, the spring is 1
Therefore, the number of parts of the clutch device and the manufacturing process can be reduced, and the clutch device can be made smaller and lighter.
また、前記クラツチバネはクラツチインナ内に
配設されているので駆動軸と被動軸との間の歯車
列にはなんらの影響もおよぼすことがなく、歯車
の径が大きくなつたり被動軸との間隔が長くなつ
たりすることがない。 In addition, since the clutch spring is located inside the clutch inner, it does not have any effect on the gear train between the drive shaft and the driven shaft. I never get used to it.
図面は本発明の一実施例を示すもので、第1図
はクラツチ装置の縦断側面図、第2図は主要部品
の分解斜視図、第3図及び第4図は作用説明図で
ある。
尚図面中1は駆動軸、2は被動軸、15cは調
整部材、cはケース、c1は点検窓、c2は蓋
体。
The drawings show one embodiment of the present invention; FIG. 1 is a longitudinal sectional side view of the clutch device, FIG. 2 is an exploded perspective view of the main parts, and FIGS. 3 and 4 are explanatory diagrams of the operation. In the drawings, 1 is a drive shaft, 2 is a driven shaft, 15c is an adjustment member, c is a case, c1 is an inspection window, and c2 is a lid.
Claims (1)
チアウタと、該クラツチアウタ内に配置され、前
記クラツチアウタに対して摺動自在なクラツチイ
ンナと、該クラツチインナと前記クラツチアウタ
との間に設けられるクラツチデイスク及びクラツ
チプレートと、前記クラツチインナの端部に一体
的に形成され、前記クラツチデイスク及びクラツ
チプレートの一端側に位置するプレツシヤプレー
トと、クラツチデイスク及びクラツチプレートの
他端側に位置するクラツチセンタと、前記被動軸
に固定される固定部材と、前記クラツチインナに
取り付けられ、前記固定部材に対して被動軸の軸
回り方向に回動可能且つ軸線方向に摺動可能な可
動部材と、該可動部材と前記クラツチインナとの
間に設けられ、前記クラツチインナ及びプレツシ
ヤプレートを前記クラツチデイスクとクラツチプ
レートの摩擦係合方向に弾圧するとともに前記可
動部材を固定部材側に弾圧するクラツチバネとか
ら成り、前記固定部材に凹カムを形成するととも
に前記可動部材に前記凹カムに係合する凸カムを
形成し、前記凹カムの深さを、駆動軸からの駆動
による可動部材の回転方向に漸次浅く形成し、前
記クラツチバネを前記クラツチインナの凹部空間
内に配置したことを特徴とするクラツチ装置。1. A clutch outer connected to the drive shaft side via a gear train, a clutch inner disposed within the clutch outer and slidable with respect to the clutch outer, and a clutch disk and clutch provided between the clutch inner and the clutch outer. a pressure plate integrally formed at an end of the clutch inner and located at one end of the clutch disk and the clutch plate; a clutch center located at the other end of the clutch disk and the clutch plate; a fixed member fixed to the driven shaft; a movable member attached to the clutch inner and rotatable in a direction around the axis of the driven shaft and slidable in the axial direction with respect to the fixed member; the movable member and the clutch inner a clutch spring provided between the clutch inner and the pressure plate in the direction of frictional engagement between the clutch disk and the clutch plate, and the movable member toward the fixed member; a convex cam that engages with the concave cam is formed on the movable member, the depth of the concave cam is gradually reduced in a direction of rotation of the movable member driven by a drive shaft, and the clutch spring is A clutch device characterized in that the clutch device is disposed within a recessed space of the clutch inner.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11004180A JPS5737123A (en) | 1980-08-11 | 1980-08-11 | Clutch device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11004180A JPS5737123A (en) | 1980-08-11 | 1980-08-11 | Clutch device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5737123A JPS5737123A (en) | 1982-03-01 |
JPH0337655B2 true JPH0337655B2 (en) | 1991-06-06 |
Family
ID=14525607
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP11004180A Granted JPS5737123A (en) | 1980-08-11 | 1980-08-11 | Clutch device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5737123A (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0674814B2 (en) * | 1983-05-27 | 1994-09-21 | ヤマハ発動機株式会社 | Friction clutch |
JPH0765628B2 (en) * | 1985-09-24 | 1995-07-19 | スズキ株式会社 | Friction clutch |
JPH0756292B2 (en) * | 1986-01-10 | 1995-06-14 | スズキ株式会社 | Back torque reduction device |
JP4691929B2 (en) * | 2004-08-30 | 2011-06-01 | スズキ株式会社 | Back torque reduction device |
JP4669359B2 (en) * | 2005-09-14 | 2011-04-13 | 株式会社エフ・シー・シー | Power transmission device |
DK1998059T3 (en) | 2005-12-21 | 2014-09-22 | Ntn Toyo Bearing Co Ltd | Roller bearing, retaining segment and support structure for a main shaft of a wind powered generator |
JP2009052746A (en) * | 2008-10-01 | 2009-03-12 | Ntn Corp | Rolling bearing, cage segment, and structure for supporting main shaft of wind power generator |
CN102141094B (en) * | 2011-01-28 | 2012-12-26 | 浙江大学 | Composite clutch |
JP6630205B2 (en) * | 2016-03-23 | 2020-01-15 | 本田技研工業株式会社 | Clutch device |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4419443Y1 (en) * | 1964-10-16 | 1969-08-20 | ||
JPS5491654A (en) * | 1977-12-28 | 1979-07-20 | Yamaha Motor Co Ltd | Friction disc type clutch |
-
1980
- 1980-08-11 JP JP11004180A patent/JPS5737123A/en active Granted
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4419443Y1 (en) * | 1964-10-16 | 1969-08-20 | ||
JPS5491654A (en) * | 1977-12-28 | 1979-07-20 | Yamaha Motor Co Ltd | Friction disc type clutch |
Also Published As
Publication number | Publication date |
---|---|
JPS5737123A (en) | 1982-03-01 |
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