JPS59495Y2 - damper disc - Google Patents
damper discInfo
- Publication number
- JPS59495Y2 JPS59495Y2 JP1147780U JP1147780U JPS59495Y2 JP S59495 Y2 JPS59495 Y2 JP S59495Y2 JP 1147780 U JP1147780 U JP 1147780U JP 1147780 U JP1147780 U JP 1147780U JP S59495 Y2 JPS59495 Y2 JP S59495Y2
- Authority
- JP
- Japan
- Prior art keywords
- plate
- circumferential surface
- outer circumferential
- hub
- bub
- 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
Landscapes
- Mechanical Operated Clutches (AREA)
Description
【考案の詳細な説明】
本考案は自動車用クラッチディスクとか舶用エンジンと
減速機の間の捩り振動吸収用ダンパー等として使用する
ことのできるダンパーディスクに関する。[Detailed Description of the Invention] The present invention relates to a damper disk that can be used as a clutch disk for automobiles, a damper for absorbing torsional vibration between a marine engine and a reduction gear, and the like.
従来のクラッチディスクをその縦断面部分略図を示す第
１図により説明すると、出力軸１にスプライン嵌合した
バブ２の外周面３，４にはバブフランジ５を挾んで環状
のクラッチプレート６ （サイドプレート）とリテイニ
ングプレート７が回転自在に嵌合している。A conventional clutch disc will be explained with reference to FIG. 1, which shows a schematic longitudinal cross-sectional view of the conventional clutch disc.A ring-shaped clutch plate 6 (side plate) is formed on the outer circumferential surface 3, 4 of a bub 2 spline-fitted to an output shaft 1, with a bub flange 5 in between. ) and the retaining plate 7 are rotatably fitted.
両プレート６．７の内、クラッチプレート６は内周縁を
バブ２の外周面３に当接させることによりバブ２に対し
て半径方向に位置決め（センタリング）しである。Of the two plates 6.7, the clutch plate 6 is positioned (centered) in the radial direction with respect to the bub 2 by bringing its inner circumferential edge into contact with the outer circumferential surface 3 of the bub 2.
又リテイニングプレート７は、ピン１４及び図示されて
いない内周部のピンを介してクラッチプレート６と連結
することによりバブ２に対して半径方向に位置決めされ
ており、ブレート７の内周縁はバブ２の外周面４に当接
していない。Further, the retaining plate 7 is positioned in the radial direction with respect to the bub 2 by being connected to the clutch plate 6 via a pin 14 and a pin on the inner circumference (not shown), and the inner circumference of the plate 7 It is not in contact with the outer circumferential surface 4 of 2.
両プレート６．７及びバブフランジ５の対応する部分に
は円周方向に間隔を隔てて複数個の窓孔８，９．１０が
設けてあり、各１組の窓孔８，９．１０には円周方向に
延びるコイルスプリング１１が配置しである。A plurality of window holes 8, 9.10 are provided in corresponding portions of both plates 6.7 and the bub flange 5 at intervals in the circumferential direction, and each pair of window holes 8, 9.10 is provided with a plurality of window holes 8, 9.10. A coil spring 11 extending in the circumferential direction is arranged.
クラッチプレート６の外周部にはクツショニングプレー
ト１２が固定され、該プレート１２０両面には環状のフ
ェーシング１３が固定しである。A cushioning plate 12 is fixed to the outer periphery of the clutch plate 6, and annular facings 13 are fixed to both sides of the plate 120.
１７はフリクションワッシャー、スプリング等からなる
環状の摩擦部材である。17 is an annular friction member consisting of a friction washer, a spring, etc.
そしてこの従来品の構造によるとフェーシング１３をフ
ライホイール１５とプレッシャープレート１６で圧縮状
態に挟持することにより、エンジンからのトルクはフラ
イホイール１５、フェーシング１３を介してクラッチプ
レート６に伝わり、プレート６及びプレート７からスプ
リング１１及び摩擦部材１７を介してフランジ５、バブ
２、出力軸１に伝わるようになっており、又その際スプ
リング１１が圧縮されるので、プレート６゜７はバブ２
に対して捩れる。According to the structure of this conventional product, by sandwiching the facing 13 between the flywheel 15 and the pressure plate 16 in a compressed state, torque from the engine is transmitted to the clutch plate 6 via the flywheel 15 and the facing 13, and The power is transmitted from the plate 7 to the flange 5, the bubble 2, and the output shaft 1 via the spring 11 and the friction member 17, and since the spring 11 is compressed at this time, the plate 6.7 is transmitted to the bubble 2.
Twisted against.
ところがプレート６がバブ２に対して捩れると、プレー
ト６の内周縁とバブ２の外周面３との間に摩擦が生じる
ので、スプリング１１及び摩擦部材１７により設定した
クラッチディスクの伝達トルク−捩り特性が変化し、所
望の振動吸収効果を得ることができなくなる恐れがあり
、又バブ外周面３が第２図の如く局部的に摩耗して上記
不具合が顕著になると共に、バブ２の耐久性が低下する
恐れがあった。However, when the plate 6 is twisted relative to the bub 2, friction occurs between the inner circumferential edge of the plate 6 and the outer circumferential surface 3 of the bub 2. There is a risk that the characteristics will change and it will not be possible to obtain the desired vibration absorption effect.Also, the outer circumferential surface 3 of the bubble 3 will wear locally as shown in Figure 2, making the above-mentioned problems noticeable, and the durability of the bubble 2 may deteriorate. There was a risk that this would decrease.
これらの不具合に対する対策として従来品ではバブ外周
面３に焼入れ焼戻しを施して外周面３の硬度を高めであ
るが、加工誤差等によりプレート６の回転中心とバブ２
の回転中心Ｏ−Ｏがずれている場合にはプレート６内周
縁がバブ外周面３に大きな圧接力で擦れるので、その場
合にはバブ外周面３が著しく摩耗してバブ２の耐久性が
大幅に低下し、又伝達トルクー捩り特性及びヒステリシ
ス特性が不安定になるという不具合を防止することがで
きなかった。As a countermeasure to these problems, in conventional products, the outer circumferential surface 3 of the bubble is quenched and tempered to increase the hardness of the outer circumferential surface 3, but due to machining errors etc., the center of rotation of the plate 6 and the bubble 2
If the center of rotation O-O is misaligned, the inner circumferential edge of the plate 6 will rub against the outer circumferential surface 3 of the bubble with a large pressing force. In addition, it was not possible to prevent the problem that the transmission torque, the torsional characteristics, and the hysteresis characteristics became unstable.
本考案は上記従来の不具合を解決することを目的として
おり、本考案においてはハブ２の外周面３に硬質メッキ
が施しである。The present invention aims to solve the above-mentioned conventional problems, and in this invention, the outer peripheral surface 3 of the hub 2 is hard plated.
硬質メッキとしてはハードクロムメッキ、触媒ニッケル
メッキ、無電解ニッケルメッキが最適であり、又その他
周知の電気的あるいは化学的硬質メッキを採用すること
もできる。As hard plating, hard chrome plating, catalytic nickel plating, and electroless nickel plating are most suitable, and other well-known electrical or chemical hard plating may also be used.
このように本考案ではハブ外周面３に硬質メッキを施し
たので、従来の焼入れ焼戻しを施した場合よりもハブ外
周面３の硬度を高めることができ、プレート６内周縁が
ハブ外周面３に大きな圧接力で擦れる場合でも、ハブ外
周面３の摩耗を可及的に防止することができ、ハブ２の
耐久性を大幅に向上させることができる。In this way, in the present invention, since hard plating is applied to the hub outer circumferential surface 3, the hardness of the hub outer circumferential surface 3 can be increased compared to the case where conventional quenching and tempering is applied, and the inner circumferential edge of the plate 6 is applied to the hub outer circumferential surface 3. Even in the case of rubbing due to a large pressure contact force, wear of the hub outer circumferential surface 3 can be prevented as much as possible, and the durability of the hub 2 can be greatly improved.
又ハブ外周面３は滑らかになるので、クラッチツブレー
ト６内周縁とパブ外周面３間の摩擦係数は小さく、従っ
てプレート６からハブ外周面３へ摩擦により伝達される
トルクは可及的に小さくなり、ディスクのヒステリシス
トルクにばら付きが生じず伝達トルク捩り特性は安定す
る。Also, since the hub outer circumferential surface 3 is smooth, the coefficient of friction between the inner circumferential edge of the clutch plate 6 and the pub outer circumferential surface 3 is small, and therefore the torque transmitted from the plate 6 to the hub outer circumferential surface 3 by friction is as small as possible. Therefore, there is no variation in the hysteresis torque of the disk, and the transmitted torque torsional characteristics are stabilized.
ハブ２としては従来の旋盤加工品をそのまま使うことが
でき、又メッキ処理も従来の焼入れ焼戻し処理と比べて
簡単に行えるので、製造コストは低い。As the hub 2, a conventional lathe-processed product can be used as is, and the plating process can be performed more easily than the conventional quenching and tempering process, so the manufacturing cost is low.
なお本考案を具体化する場合にはハブ外周面４だけに硬
質メッキを施し、外周面４にリテイニングプレ−１・７
の内周縁を当接させて半径方向の位置決めを行うと共に
、クラッチプレート６の内周縁とハブ外周面３の間に僅
がな隙間を隔てることもできる。In addition, when embodying the present invention, hard plating is applied only to the outer circumferential surface 4 of the hub, and retaining plates 1 and 7 are applied to the outer circumferential surface 4.
It is also possible to perform radial positioning by bringing the inner circumferential edges of the clutch plate 6 into contact with each other, and to provide a slight gap between the inner circumferential edge of the clutch plate 6 and the hub outer circumferential surface 3.
外周面３又は外周面４の内、プレート６又は７が当接す
る部分だけに硬質メッキを施すこともできる。It is also possible to apply hard plating only to the portion of the outer circumferential surface 3 or the outer circumferential surface 4 that is in contact with the plate 6 or 7.
ハブ２全体に硬質メッキを施すこともでき、その場合に
はハブ２全体の表面硬度が増加し、スプリング１１の両
端が圧接する窓孔１゜の縁の摩耗が防止され、又スプラ
イン歯１８の摩耗が防止されるので、この点においても
ハブ２の耐久性を向上させることができる。It is also possible to apply hard plating to the entire hub 2. In that case, the surface hardness of the entire hub 2 increases, the wear of the edge of the window hole 1° where both ends of the spring 11 are pressed is prevented, and the spline teeth 18 are also coated with hard plating. Since wear is prevented, the durability of the hub 2 can be improved in this respect as well.
なお触媒ニッケルメッキや無電解ニッケルメッキを採用
した場合には、メッキ処理後に熱処理を施すことにより
クロムメッキよりも高い硬度を得ることができる。Note that when catalytic nickel plating or electroless nickel plating is used, higher hardness than chrome plating can be obtained by heat treatment after plating.
第１図は従来のクラッチディスク及び本考案によるメッ
キ部分を示す縦断面部分略図、第２図は摩耗状態を示す
ためのスプラインハブの縦断面部分図である。
２・・・スプラインハブ、３，４・・・外周面、６・・
・クラッチプレート（サイドプレート）、７・・・リテ
イニングプレート。FIG. 1 is a partial vertical cross-sectional view showing a conventional clutch disc and a plated portion according to the present invention, and FIG. 2 is a partial vertical cross-sectional view of a spline hub to show the state of wear. 2...Spline hub, 3, 4...Outer peripheral surface, 6...
・Clutch plate (side plate), 7... Retaining plate.
Claims (1)
を環状に施し、上記メッキ部分に環状のサイドプレート
又はリテイニングプレートの一方（第１ブレート）の内
周縁を回転自在に当接させ、上記第１プレートに他方の
第２プレートを固定し、第２プレートの内周縁を隙間を
隔ててバブに嵌合させたことを特徴とするダンパーディ
スク。At least a part of the outer peripheral surface of the spline bub is annularly coated with hard plating, and the inner peripheral edge of one of the annular side plate or the retaining plate (first plate) is brought into rotatable contact with the plated part, and the first A damper disk characterized in that the other second plate is fixed to the plate, and the inner peripheral edge of the second plate is fitted into the bub with a gap in between.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1147780U JPS59495Y2 (en) | 1980-01-31 | 1980-01-31 | damper disc |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1147780U JPS59495Y2 (en) | 1980-01-31 | 1980-01-31 | damper disc |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS56113234U JPS56113234U (en) | 1981-09-01 |
| JPS59495Y2 true JPS59495Y2 (en) | 1984-01-09 |
Family
ID=29608087
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1147780U Expired JPS59495Y2 (en) | 1980-01-31 | 1980-01-31 | damper disc |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59495Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1985000858A1 (en) * | 1983-08-10 | 1985-02-28 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Spring-type clutch disk |
-
1980
- 1980-01-31 JP JP1147780U patent/JPS59495Y2/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1985000858A1 (en) * | 1983-08-10 | 1985-02-28 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Spring-type clutch disk |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS56113234U (en) | 1981-09-01 |
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