JPS60201122A - Damper disc - Google Patents
Damper discInfo
- Publication number
- JPS60201122A JPS60201122A JP5894284A JP5894284A JPS60201122A JP S60201122 A JPS60201122 A JP S60201122A JP 5894284 A JP5894284 A JP 5894284A JP 5894284 A JP5894284 A JP 5894284A JP S60201122 A JPS60201122 A JP S60201122A
- Authority
- JP
- Japan
- Prior art keywords
- working fluid
- flange
- cases
- fluid reservoir
- reservoir
- 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.)
- Granted
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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/1217—Motion-limiting means, e.g. means for locking the spring unit in pre-defined positions
- F16F15/1218—Motion-limiting means, e.g. means for locking the spring unit in pre-defined positions by means of spring-loaded radially arranged locking means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は内部に作動流体溜めを形成したダンパーディス
クに係シ、特に駆動系の捩り作動を効果的に吸収して継
続フィーリングを向上させるようにしたものに関する。DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a damper disk that has a working fluid reservoir formed therein, and in particular effectively absorbs torsional motion of the drive system to improve the continuous feeling. Concerning what was done.
（従来例）
従来から、この種ダンパーディスクには流体式ショック
アブソーバを内蔵して、駆動系の捩シ振動を吸収するよ
うにしたものが知られているが（例えば、特開昭５６−
１２０８４４号）、流体式ショックアブソーバでは、捩
り振動を有効に吸収し得る固有のヒステリシスを安定し
て発生させるオリフィス機構を設けることが困難であシ
、また、オリフィス機構そのものも捩シ角度が変化して
も一定のヒステリシスのみしか発生させ得す、捩り振動
を効果的に吸収できないという不具合が発生している。(Conventional Example) Conventionally, this type of damper disk has a built-in fluid shock absorber to absorb torsional vibrations of the drive system (for example, Japanese Patent Application Laid-Open No. 1983-1999)
120844), it is difficult to provide an orifice mechanism that stably generates the inherent hysteresis that can effectively absorb torsional vibrations in a fluid type shock absorber, and the orifice mechanism itself also changes in torsional angle. However, there are problems in that only a certain amount of hysteresis can occur, and torsional vibrations cannot be effectively absorbed.
（発明の目的）
本発明は以上の不具合を考慮してなされたものであって
、その目的とするところは、捩シ振動全有効に吸収し得
る作動流体溜めを内蔵するとともに、その作動流体溜め
で発生するヒステリシスを捩り角度の増加につれて増大
させることができるダンパーディスクを提供する点にあ
る。(Object of the Invention) The present invention has been made in consideration of the above-mentioned problems, and its purpose is to provide a built-in working fluid reservoir that can effectively absorb all of the torsional vibrations, and to The object of the present invention is to provide a damper disk that can increase the hysteresis generated in the damper disk as the twist angle increases.
（発明の構成）
上記目的全達成すべく、本発明によるダンパーディスク
の構成は、外周部にトルクが導入されるケースと該ケー
スの外周に設けられたスペーサとによフスプラインハブ
のフランジを液密状態に覆い、フランジの窓孔と該窓孔
に対向するケースの窪みにトーションスプリングを配置
してフランジとケースとを連結し、該フランジの周縁部
を切欠いて作動流体溜めを形成し、前記スペーサの内周
に作動流体溜め内に突出する突起を設け、該突起の先端
と作動流体溜めの内周面との間の間隙が前記ケースとフ
ランジの捩シ角の増大に伴なって減少するように前記作
動流体溜めの内周面を形成し、ケース内に作動流体を満
たしたことを要旨とするものである。(Structure of the Invention) In order to achieve all of the above objects, the damper disk according to the present invention has a structure in which the flange of the spline hub is damped by a case into which torque is introduced into the outer periphery and a spacer provided on the outer periphery of the case. A torsion spring is disposed in the window hole of the flange and a recess in the case opposite to the window hole to connect the flange and the case, and the peripheral edge of the flange is cut out to form a working fluid reservoir. A protrusion that protrudes into the working fluid reservoir is provided on the inner periphery of the spacer, and the gap between the tip of the protrusion and the inner peripheral surface of the working fluid reservoir decreases as the torsional angle between the case and the flange increases. The gist is that the inner circumferential surface of the working fluid reservoir is formed in such a manner that the case is filled with working fluid.
（実施例）
以下、図面を参照して本発明の一実施例を説明する。第
１図は本発明全適用したクラッチディスクの第２図にお
ける２−０−２縦断面を示している。第１図において、
図示されていない出力軸にスプライン嵌合するスプライ
ンハブ１のフランジ２は両側から１対のケース８，４で
覆われている。(Example) Hereinafter, an example of the present invention will be described with reference to the drawings. FIG. 1 shows a 2-0-2 vertical section in FIG. 2 of a clutch disk to which the present invention is fully applied. In Figure 1,
A flange 2 of a spline hub 1 that is spline-fitted to an output shaft (not shown) is covered with a pair of cases 8 and 4 from both sides.
ケース３．４はフランジ２よシも外径が犬きぐ、両ケー
ス８，４の外周部は環状のスペーサ５．サブグレート６
、クツショニングプレート７および環状パツキン８を挾
んでリベット９によシ液密を保持して一体に連結されて
いる。１０はリベット１１によシクツショニングプレー
ト７に固定された７エーシングである。ケース３，４の
内周縁には外向きに延びる筒状フランジ１２．１１が形
成してあり、フランジ１２．１８はハブ１の外周面上の
環状溝に嵌合したシール１４に接している。The outer diameter of the case 3.4 is also the same as that of the flange 2, and the outer periphery of both cases 8 and 4 has an annular spacer 5.4. Sub Great 6
, the cushioning plate 7 and the annular packing 8 are sandwiched between them and are integrally connected to each other by rivets 9 in a liquid-tight manner. Reference numeral 10 designates an ace 7 fixed to the suctioning plate 7 by rivets 11. An outwardly extending cylindrical flange 12.11 is formed on the inner periphery of the cases 3, 4, the flange 12.18 abutting a seal 14 fitted in an annular groove on the outer periphery of the hub 1.
そして、ケース８，４内には高粘性の作動流体であるシ
リコンオイルが満たされている。１５ 、１６は同志に
配置された小径および大径の圧縮コイルスプリング（ト
ーションスプリング）で、第１図の一部切欠き■矢視図
である第２図の如く、フランジ２に内周方向に１８０°
間隔を隔てて設けた２個の窓孔１７にそれぞｆ′Ｌ１組
のスプリング１５゜１６が配置されている。このスプリ
ング１５の両端はスプリングシート１８に圧接し、スプ
リング１６はスプリングシー）１ｇの外周に設けられて
おり、ケース３，４がフランジ２に対して捩れていない
図示の状態において各スプリングシート１８はフランジ
２の窓孔１７の両側縁に形成された突起部１７ａに当接
している。また、フランジ２には窓孔１７と円周方向に
９０°間隔を隔てて２個の窓孔１９が設けられておシ、
これらの窓孔１９にはそれぞれ前記スプリング１６より
もさらに大径のコイルスプリング（トーションスプリン
グ）２０が配置されている。このスプリング２０は対応
した位置に窓孔６ａ２有する前記サブプレート６で支持
されておシ、ケース３，４がフランジ２に対して捩れて
いない図示の状態において、スプリング２０の両端と窓
孔１９の両側線との間に等間隔２隔てた位置、すなわち
窓孔１９の円周方向中央位置にスプリング２０が位置決
めされている。The cases 8 and 4 are filled with silicone oil, which is a highly viscous working fluid. 15 and 16 are small-diameter and large-diameter compression coil springs (torsion springs) arranged together, and as shown in Fig. 2, which is a partially cutaway view of Fig. 180°
F'L1 sets of springs 15 and 16 are arranged in two window holes 17 provided at intervals, respectively. Both ends of the spring 15 are in pressure contact with the spring seats 18, and the springs 16 are provided on the outer periphery of the spring seats 1g.In the illustrated state where the cases 3 and 4 are not twisted relative to the flange 2, each spring seat 18 is It abuts against protrusions 17a formed on both side edges of the window hole 17 of the flange 2. Further, the flange 2 is provided with two window holes 19 spaced apart from each other by 90 degrees in the circumferential direction from the window hole 17.
Coil springs (torsion springs) 20 having a larger diameter than the spring 16 are arranged in each of these window holes 19 . This spring 20 is supported by the sub-plate 6 which has a window hole 6a2 at a corresponding position. The spring 20 is positioned at two equal intervals from both sides, that is, at the center of the window hole 19 in the circumferential direction.
さらに、フランジ２の周縁部における窓孔１７゜１９の
中間位置には円周方向に９０°間隔全隔てて、フランジ
２を切欠いて形成した４個の作動流体溜め２１が設けら
れておシ、これらの作動流体溜め２１内にはそれぞれス
ペーサ５の内周面から連続して一体に突出された４個の
突起５ａが設けられている。これらの突起５ａも円周方
向に９０°間隔を隔てて設けられておシ、図示の捩れ角
がＯの中立位置で、突起５ａは作動流体溜め２１の中央
に配置しである。作動流体溜め２１の内周面２２は中立
軸（中立時における突起５ａの中心線）から±ａ０の範
囲で突起５ａの先端との間に、比較的大きなりリアラン
スを形成する牛円形をなし、中立軸から±ａ０〜±Ｃ０
の範囲で突起５ａの先端との間に極く小さなりリアラン
スＣ＋’に形成する円弧状をなし、中立軸から±００の
位置に半径方向に沿った側壁２２ａを設けである。また
、フランジ２の窓孔１７の両側縁とスプリング１６の両
端との位相差もａｏに設定してあシ、窓孔１９の両側縁
とスプリング２０の両端との位相差はｂｏに設定してあ
シ、コレらａＯ、ｂｏ 、 ＣＯの関係は
ａｏ＜ｂｏ＜００
に設定しである。さらに、スプリング１５，１６゜２０
の窓孔１７，１９から第１ｒｉ！Ｊにおいて左右に張り
出した部分は、両ケース８，４に設けたスプリング１６
．２０に概ね対応する形状の窪み２３゜２４で覆われて
いる。前記スプリングシー）１８は窪み２３．２４（ス
プリング１５．１６の設置空間）の端壁内面にスプリン
グ１５．１６で押圧されており、スプリングシート１８
の端面１８ａは窪み２３．２４に圧接している。Further, four working fluid reservoirs 21 formed by cutting out the flange 2 are provided at the intermediate positions between the window holes 17 and 19 at the peripheral edge of the flange 2, at intervals of 90 degrees in the circumferential direction. In each of these working fluid reservoirs 21, four protrusions 5a are provided which continuously and integrally protrude from the inner circumferential surface of the spacer 5. These protrusions 5a are also provided at intervals of 90° in the circumferential direction, and in the neutral position where the illustrated twist angle is O, the protrusions 5a are arranged at the center of the working fluid reservoir 21. The inner circumferential surface 22 of the working fluid reservoir 21 has a circular shape that forms a relatively large clearance between the tip of the protrusion 5a and the tip of the protrusion 5a in the range of ±a0 from the neutral axis (the center line of the protrusion 5a in the neutral state), ±a0 to ±C0 from neutral axis
A side wall 22a is provided along the radial direction at a position of ±00 from the neutral axis, forming an arc with an extremely small clearance C+' between the tip of the protrusion 5a and the end of the projection 5a. Additionally, the phase difference between both side edges of the window hole 17 of the flange 2 and both ends of the spring 16 is set to ao, and the phase difference between both side edges of the window hole 19 and both ends of the spring 20 is set to bo. The relationship between ao, bo, and CO is set to ao<bo<00. Furthermore, springs 15, 16° 20
1st ri from window holes 17 and 19! The parts that protrude left and right at J are springs 16 provided in both cases 8 and 4.
．． It is covered with depressions 23 and 24 whose shape roughly corresponds to that of 20. The spring seat 18 is pressed by a spring 15.16 against the inner surface of the end wall of the recess 23.24 (installation space for the spring 15.16).
The end face 18a of is in pressure contact with the depression 23.24.
次に動作を説明する。第１図に示す如く、本発明全クラ
ッチディスクに適用した場合、このクラッチを接続し、
図示されていないフライホイールから第２図のクラッチ
回転方向Ａのトルクが７エーシングｌＯに伝わると、該
トルクはクツショニングプレート７を介してケース３，
４に導入され、さらに窪み２Ｂ、２４の反回転方向側の
端壁内面からスプリング１５．１６．２（ｌ介して窓孔
１７゜１９の回転方向Ａ側の側線に伝わり、フランジ２
からハブｌ、出力軸へと伝わる。その際、捩九角りがｏ
−ａｏの範囲ではスプリング１５のみが圧縮され、ａ
０〜ｂｏの範囲ではスプリング１５．１６が圧縮さ九、
ｂ０〜Ｃ０の範囲ではスプリング１５゜１６．２０が圧
縮されながら、ケース８．４が回転方向Ａに捩れる。第
８図の特性ｘｔｉスプリング１５．１６．２０のみを介
して伝達されるトルクＴと捩れ角りとの関係を示してい
るが、０〜ａ０の範囲ではスプリング１５の伝達トルク
は無視し得る程度に微小であり、０−ａｏ、 ａ’ 〜
ｂ’、 ｂ’ 〜Ｃ！’の各範囲内でトルクＴと捩れ角
りとは比例している。Next, the operation will be explained. As shown in FIG. 1, when the present invention is applied to all clutch discs, this clutch is connected,
When torque in the clutch rotation direction A shown in FIG.
4, and is further transmitted from the inner surface of the end wall on the counter-rotation direction side of the recesses 2B and 24 to the side line on the rotation direction A side of the window hole 17°19 through the spring 15.16.2 (l), and
It is transmitted from the hub l to the output shaft. At that time, the nine-corner corner of the screw is o.
In the range -ao, only the spring 15 is compressed, and a
In the range of 0 to bo, the spring 15.16 is compressed9,
In the range b0 to C0, the case 8.4 is twisted in the rotational direction A while the spring 15°16.20 is compressed. Figure 8 shows the relationship between the torque T transmitted only through the characteristic 0-ao, a' ~
b', b' ~C! Within each range of ', the torque T and the twist angle are proportional.
一方、第２図においてケース３．４が回転方向Ａに移動
すると、スペーサ５の突起５ａ４Ａ方向に作動流体溜め
２１内で移動する。この際、０〜ａ０の範囲内では、突
起５ａの先端と作動流体溜め２１の内周面とのクリアラ
ンスが比較的大きく設定されているので、内部のシリコ
ンオイルの圧縮および押出しによる抵抗力ははとんど発
生しない。On the other hand, when the case 3.4 moves in the rotational direction A in FIG. 2, it moves within the working fluid reservoir 21 in the direction of the projection 5a4A of the spacer 5. At this time, within the range of 0 to a0, the clearance between the tip of the protrusion 5a and the inner peripheral surface of the working fluid reservoir 21 is set relatively large, so the resistance force due to compression and extrusion of the internal silicone oil is small. It almost never happens.
やがて、捩れ角りがａｏに達すると、突起５ａの先端と
作動流体溜め２１の内周面とのクリアランスは極く僅か
なＣ１となるので、シリコンオイルの圧縮および押出し
による抵抗力が突起５ａとフランジ２に伝わる。また、
捩り行程中にクリアランスＣ１以外の他の隙間、すなわ
ち各プレート間。Eventually, when the torsion angle reaches ao, the clearance between the tip of the protrusion 5a and the inner circumferential surface of the working fluid reservoir 21 becomes extremely small C1, so that the resistance force due to compression and extrusion of the silicone oil is applied to the protrusion 5a. It is transmitted to flange 2. Also,
During the twisting stroke, other gaps other than the clearance C1, i.e. between each plate.
スペーサ５とフランジ２との間からシリコンオイルが漏
出するが、シリコンオイルは高粘性であるので、上記の
隙間から漏出するシリコンオイルは極〈微量であり、そ
の影響けは、とんど無視できる程度である。Silicone oil leaks from between the spacer 5 and flange 2, but since silicone oil is highly viscous, the amount of silicone oil that leaks from the above gap is extremely small and its influence can be ignored. That's about it.
このようにケース３．４の捩れに対してシリコンオイル
による抵抗力が加わると、その抵抗力に応じたトルクが
シリコンオイルを介して（スプリング１５，１６．２０
を介さずに）ケース３，４からフランジ２に伝達され、
第３図の如く実際の伝達トルク特性は前記特性Ｘにヒス
テリシスｈが加重されて特性Ｙになる。第３図の特性Ｙ
は捩り角速度が一定の場合を示しているが、ケース８゜
４の捩り角速度が変化すると、作動流体溜め２１内のシ
リコンオイルに加えられる圧縮力が変化するので、捩り
に対するシリコンオイルの抵抗力も変化し、したがって
ヒステリシスｈも捩夛角速度に対応して変化する。In this way, when the resistance force due to the silicone oil is applied to the twisting of the case 3.4, a torque corresponding to the resistance force is applied via the silicone oil (springs 15, 16, 20
) is transmitted from cases 3 and 4 to flange 2,
As shown in FIG. 3, the actual transmission torque characteristic becomes characteristic Y by adding hysteresis h to characteristic X. Characteristic Y in Figure 3
shows the case where the torsional angular velocity is constant, but as the torsional angular velocity of the case 8°4 changes, the compressive force applied to the silicone oil in the working fluid reservoir 21 changes, so the resistance force of the silicone oil against torsion also changes. Therefore, the hysteresis h also changes in accordance with the torsional angular velocity.
なお、振力角度りが００になると、突起５ａの側面が作
動流体溜め２１の内周面２２に当接し、それ以上の捩ｆ
′Ｌは阻止される。Note that when the vibration force angle reaches 00, the side surface of the protrusion 5a comes into contact with the inner circumferential surface 22 of the working fluid reservoir 21, and further torsion f
'L is blocked.
（発明の効果）
以上説明したよりに、本発明によるダンパーディスクで
は、ケース８．４内にシリコンオイルを満たし、フラン
ジ２０周級部に作動流体溜め２１を設け、この作動流体
溜め２１内に突出する突起５ａｋスペーサ５に設け、作
動流体溜め２１の内周面２２と突起５ａの先端との間隙
が捩り角の増大に伴なって減少するように前記内周面２
２を形成したので、振力角度の増大に伴なってヒステリ
シストルクを増加させることができ、発進・停止時、高
速運転時にも常にトルク変動および振動を効果的に吸収
することができる。また、作動流体の粘性を変更するこ
とにより簡単にヒステリシス特性を調整することかでき
、用途に応じて最適のダンパーディスクとすることがで
きる。しかも、前記−実施例においては捩フ角りの増大
に伴なってスプリング１５，１６．２０が順次圧縮され
るようになっているので、第８図の特性Ｙは捩り角ａＯ
、’ｂｏで段階的に傾斜角度が急になシ、一層クラッチ
断続時のフィーリングを向上させることができる。(Effects of the Invention) As explained above, in the damper disk according to the present invention, the case 8.4 is filled with silicone oil, the working fluid reservoir 21 is provided around the flange 20, and the damper disk protrudes into the working fluid reservoir 21. A protrusion 5ak is provided on the spacer 5 so that the inner circumferential surface 2 is provided so that the gap between the inner circumferential surface 22 of the working fluid reservoir 21 and the tip of the protrusion 5a decreases as the torsion angle increases.
2, it is possible to increase the hysteresis torque as the vibration angle increases, and it is possible to effectively absorb torque fluctuations and vibrations at all times even during starting/stopping and high-speed operation. In addition, the hysteresis characteristics can be easily adjusted by changing the viscosity of the working fluid, and the damper disk can be optimized depending on the application. Moreover, in the embodiment described above, the springs 15, 16, and 20 are sequentially compressed as the torsion angle increases, so that the characteristic Y in FIG.
, 'bo' makes the inclination angle steeper in stages, further improving the feeling when the clutch is engaged and engaged.
（別の実施例）
←）作動流体溜め２１は必ずしも４個のものに限らず、
例えば第４図に示すように１作動流体溜め２１の容積を
倍増して円周方向に１８０°″間隔を隔てて２個の作動
流体溜め２１を設けてもよい。(Another embodiment) ←) The number of working fluid reservoirs 21 is not necessarily limited to four,
For example, as shown in FIG. 4, the volume of one working fluid reservoir 21 may be doubled to provide two working fluid reservoirs 21 spaced apart by 180° in the circumferential direction.
（ｂ） 作動流体溜め２１の内周面２２の形状は第２図
、第８図に示すように、捩り角ａ０でクリアランスがＣ
１に減少するものに限らず、例えば第５図に示すように
、捩り角りの増大につｎてクリアランスがＣｏ 、 Ｃ
】＋ Ｃ２に段階的に減少するようにして、いわゆる多
段ヒステリシス特性を発生させることもできる。(b) The shape of the inner circumferential surface 22 of the working fluid reservoir 21 is such that the clearance is C at the torsion angle a0, as shown in FIGS. 2 and 8.
For example, as shown in FIG. 5, as the torsion angle increases, the clearance decreases to
It is also possible to generate a so-called multi-stage hysteresis characteristic by decreasing stepwise to +C2.
第１図ないし第３図は本発明の一実施例を示す図で、第
１図はダンパーディスクの縦断面図、第２図は一部を切
シ欠いて示す第１図のＩ矢視図、第８図は伝達トルク−
捩り角物性を示すグラフ、第４図は別の実施例を示す一
部を切り欠いて軸方向から見た部分図、第５図はさらに
別の実施例を示す作動流体溜めの内周面の部分図である
。ｌ・・・スプラインハブ、２・・・フランジ、８，４
・・・ケース、５・・・スペーサ、５ａ・・・突起、１
５，１６．２０・・・コイルスプリング（トーションス
プリンク）、１７゜１９・・・窓孔、２１・・・作動流
体溜め、２２・・・内周面第１図
２
ａ
第５はＩ1 to 3 are diagrams showing one embodiment of the present invention, in which FIG. 1 is a vertical sectional view of a damper disk, and FIG. 2 is a partially cutaway view taken in the direction of arrow I in FIG. 1. , Figure 8 shows the transmitted torque -
A graph showing torsional angle physical properties. Fig. 4 is a partially cutaway view of another embodiment seen from the axial direction. Fig. 5 is a graph showing the inner circumferential surface of a working fluid reservoir showing yet another embodiment. It is a partial diagram. l... Spline hub, 2... Flange, 8, 4
...Case, 5...Spacer, 5a...Protrusion, 1
5,16.20...Coil spring (torsion spring), 17°19...Window hole, 21...Working fluid reservoir, 22...Inner peripheral surface Fig. 1 2a 5th is I
Claims (1)
設けられたスペーサとによシスプラインハブのフランジ
を液密状態に覆い、フランジの窓孔と該窓孔に対向する
ケースの窪みにトーションスプリングを配置してフラン
ジとケースとを連結し、該フランジの周縁部を切欠いて
作動流体溜めを形成し、前記スペーサの内周に作動流体
溜め内に突出する突起を設け、該突起の先端と作動流体
溜めの内周面との間の間隙が前記ケースとフランジの捩
シ角の増大に伴なって減少するよ′うに前記作動流体溜
めの内周面を形成し、ケース内に作動流体を満たしたこ
とを特徴とするダンパーディスク。The flange of the spline hub is covered in a liquid-tight state by a case into which torque is introduced to the outer periphery and a spacer provided on the outer periphery of the case, and torsion is applied to the window hole of the flange and the recess of the case opposite to the window hole. A spring is arranged to connect the flange and the case, a working fluid reservoir is formed by cutting out the peripheral edge of the flange, a projection is provided on the inner periphery of the spacer that projects into the working fluid reservoir, and the tip of the projection and The inner circumferential surface of the working fluid reservoir is formed such that the gap between the inner circumferential surface of the working fluid reservoir and the inner circumferential surface of the working fluid reservoir decreases as the torsional angle between the case and the flange increases, and the working fluid is introduced into the case. A damper disc characterized by filling.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5894284A JPS60201122A (en) | 1984-03-26 | 1984-03-26 | Damper disc |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5894284A JPS60201122A (en) | 1984-03-26 | 1984-03-26 | Damper disc |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60201122A true JPS60201122A (en) | 1985-10-11 |
| JPH0143172B2 JPH0143172B2 (en) | 1989-09-19 |
Family
ID=13098881
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5894284A Granted JPS60201122A (en) | 1984-03-26 | 1984-03-26 | Damper disc |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60201122A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS636243A (en) * | 1986-06-19 | 1988-01-12 | バレオ | Damper type flywheel proper for torque transmission gear |
| FR2601741A1 (en) * | 1986-07-19 | 1988-01-22 | Fichtel & Sachs Ag | TORSIONAL OSCILLATOR WITH LUBRICANT FILLING AND HYDRAULIC LIMIT STOP |
| JPS63149447A (en) * | 1986-12-13 | 1988-06-22 | Atsugi Motor Parts Co Ltd | Torsion damper |
| WO1991003665A1 (en) * | 1989-08-29 | 1991-03-21 | Kabushiki Kaisha Daikin Seisakusho | Viscous liquid damper |
| WO1991010078A1 (en) * | 1989-12-22 | 1991-07-11 | Kabushiki Kaisha Daikin Seisakusho | Liquid viscous damper |
| CN109642620A (en) * | 2016-09-02 | 2019-04-16 | 株式会社艾科赛迪 | Die clutch construction body and clutch disk assemble body |
-
1984
- 1984-03-26 JP JP5894284A patent/JPS60201122A/en active Granted
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS636243A (en) * | 1986-06-19 | 1988-01-12 | バレオ | Damper type flywheel proper for torque transmission gear |
| FR2601741A1 (en) * | 1986-07-19 | 1988-01-22 | Fichtel & Sachs Ag | TORSIONAL OSCILLATOR WITH LUBRICANT FILLING AND HYDRAULIC LIMIT STOP |
| JPS63149447A (en) * | 1986-12-13 | 1988-06-22 | Atsugi Motor Parts Co Ltd | Torsion damper |
| WO1991003665A1 (en) * | 1989-08-29 | 1991-03-21 | Kabushiki Kaisha Daikin Seisakusho | Viscous liquid damper |
| US5097722A (en) * | 1989-08-29 | 1992-03-24 | Kabushiki Kaisha Daikin Seisakusho | Liquid viscous damper |
| DE4091513C1 (en) * | 1989-08-29 | 1993-09-30 | Daikin Mfg Co Ltd | Liquid proportional damper |
| WO1991010078A1 (en) * | 1989-12-22 | 1991-07-11 | Kabushiki Kaisha Daikin Seisakusho | Liquid viscous damper |
| DE4092383C1 (en) * | 1989-12-22 | 1995-08-17 | Daikin Mfg Co Ltd | Fluid damper for connecting flywheel discs to gearbox input shafts |
| CN109642620A (en) * | 2016-09-02 | 2019-04-16 | 株式会社艾科赛迪 | Die clutch construction body and clutch disk assemble body |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0143172B2 (en) | 1989-09-19 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |