JPS63101537A - Torsional vibration damping device - Google Patents
Torsional vibration damping deviceInfo
- Publication number
- JPS63101537A JPS63101537A JP24606886A JP24606886A JPS63101537A JP S63101537 A JPS63101537 A JP S63101537A JP 24606886 A JP24606886 A JP 24606886A JP 24606886 A JP24606886 A JP 24606886A JP S63101537 A JPS63101537 A JP S63101537A
- Authority
- JP
- Japan
- Prior art keywords
- hub
- arms
- compression spring
- drive
- arm
- 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
- 238000013016 damping Methods 0.000 title claims description 13
- 230000006835 compression Effects 0.000 claims abstract description 52
- 238000007906 compression Methods 0.000 claims abstract description 52
- 230000000717 retained effect Effects 0.000 claims description 4
- 239000000463 material Substances 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 3
- 239000002184 metal Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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
- F16F15/12—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
- F16F15/123—Wound springs
- F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
- F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
- F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
- F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
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
本発明は自動車用手動変速機のクラッチやトルクコンパ
ータを用いる自動変速機のロックアツプクラッチ等に施
用される捩り振動減衰装置に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a torsional vibration damping device used in clutches of manual transmissions for automobiles, lock-up clutches of automatic transmissions using torque converters, and the like.
従来の技術
自動車のエンジンから生ずる捩り振動は、動力伝達系に
好ましくない振動或いは騒音などを招来させる。このた
め前記クラッチには円周方向１こ作用する圧縮ばねを用
いる捩り振動減衰装置を施用することがよく知られてい
る。而して、このような捩り振動減衰装置での現状の問
題点の一つは、その装置が比較的小さい撓み範囲（振幅
）しか許容できないことである。BACKGROUND OF THE INVENTION Torsional vibrations generated from an automobile engine cause undesirable vibrations or noise in a power transmission system. For this reason, it is well known that the clutch is equipped with a torsional vibration damping device using a compression spring that acts once in the circumferential direction. One of the current problems with such torsional vibration damping devices is that they can only tolerate a relatively small deflection range (amplitude).
そこで、第３図〜第４図に示すように、ハブ３０に形成
した外方に向って突出する複数のハブアーム３１の外周
に、略環状の釣合装置３２を回動可能に配設し、この釣
合装置３２の環状部３３から半径方向内方に向うアーム
３４を前記ハブ３０の隣合うハブアーム３１．３１間に
延在させ、これらアーム３４及びハブアーム３１ 、３
１間に圧縮ばね３５ 、３５を配設して、前記ハブ３０
の隣合うハブアーム３１ 、３１間で前記圧縮ばね３５
、３５を直列に作用するばね群として構成し、前記圧
縮はね３５ 、３５に係合するドライブプレー）３６Ｌ
、３６１）の相対回動角度を増大させるようにしたもの
が本件出願人によって提案されている（特開昭５９−２
２２６２４号公報参照）。Therefore, as shown in FIGS. 3 and 4, a substantially annular balancing device 32 is rotatably disposed on the outer periphery of a plurality of outwardly projecting hub arms 31 formed on the hub 30. Arms 34 extending radially inwardly from the annular portion 33 of this balancing device 32 extend between adjacent hub arms 31 , 31 of the hub 30 .
compression springs 35, 35 are disposed between the hub 30
The compression spring 35 is connected between the adjacent hub arms 31 and 31.
, 35 as a group of springs acting in series, and a drive play (36L) that engages the compression springs 35, 35.
, 361) in which the relative rotation angle is increased has been proposed by the applicant (Japanese Patent Laid-Open No. 59-2
(See Publication No. 22624).
発明が解決しようとする問題点
このような従来の捩り振動減衰装置は、圧縮ばね３５
、３５のばね力をハブアーム３１により受けるため、ハ
ブアーム３１のばね力作用方向に対する曲げ剛性やせん
断強さを確保しなければならない。そのため、ハブ３０
の圧縮ばね３５ 、３５を収容する円周方向スペースを
拡大することにより、圧縮はね３５゜３５のより長い撓
み振幅を得ることに限界があった。Problems to be Solved by the Invention Such a conventional torsional vibration damping device uses a compression spring 35.
, 35 are received by the hub arm 31, it is necessary to ensure bending rigidity and shear strength of the hub arm 31 in the direction in which the spring force is applied. Therefore, hub 30
By enlarging the circumferential space accommodating the compression springs 35, 35, there has been a limit to obtaining longer deflection amplitudes of the compression springs 35.
そこで、本発明はより長い撓み振幅が得られる捩り振動
減衰装置を提供することを目的とする。Therefore, an object of the present invention is to provide a torsional vibration damping device that can obtain a longer deflection amplitude.
問題点を解決するための手段
入力部材に連結される略環状の駆動部材が、出力部材に
連結されるハブよりも径方向外方の離隔した位置にこの
ハブと同芯状に配置されてハブと共に左右一対のドライ
ブプレート間に相対回動可能に挾持され、かつ、この駆
動部材は内周に円周方向等間隔に斐出する複数個の駆動
アームを備え、この駆動アーム間に第１圧縮ばねが円周
方向に収容、保持されていて、この第１圧縮ばねにドラ
イブプレートがこれに形成した窓をもって係合する一方
、ハブは外周に円周方向等間隔に突出する複数個のハブ
アームを有し、このハブアームの外周には、内周にハブ
の隣合うハブアーム間に延出する釣合アームを円周方向
等間隔に突設した略環状の釣合装置が回動可能に外嵌さ
れ、この釣合アームとハブアームとの間に第２圧縮ばね
が円周方向に収容、保持されて、ハブの隣合うハブアー
ム間で直列に作用するばね群を形成し、ドライブプレー
トがハブの隣合うハブアーム間の円周方向長さと同一の
円周方向長さの窓をもって第２圧縮ばねに係合されてい
る。A substantially annular drive member connected to the input member is disposed concentrically with the hub at a distance radially outward than the hub connected to the output member. The drive member is sandwiched between a pair of left and right drive plates so as to be relatively rotatable, and this drive member is provided with a plurality of drive arms protruding from the inner periphery at equal intervals in the circumferential direction, and a first compressor is connected between the drive arms. A spring is circumferentially housed and retained, and the drive plate engages the first compression spring with a window formed therein, while the hub has a plurality of circumferentially equally spaced hub arms protruding from the outer periphery. A substantially annular balancing device is rotatably fitted on the outer periphery of the hub arm, and the substantially annular balancing device has balancing arms projecting from the inner periphery at equal intervals in the circumferential direction and extending between adjacent hub arms of the hub. , a second compression spring is circumferentially housed and retained between the counterbalancing arm and the hub arm to form a group of springs acting in series between adjacent hub arms of the hub; The second compression spring is engaged with a window having the same circumferential length as the circumferential length between the hub arms.
作用
駆動部材に入力された駆動力は、駆動部材が回動するこ
とによって駆動部材の駆動アームが第１圧縮ばねを押圧
し、この第１圧縮ばねを介してドライブプレートに伝達
され、次いで、ドライブプレートの窓の一端が第２圧縮
ばねを押圧してこれらを圧縮し、これら第２圧縮ばねを
介してノ１ブに伝達される。このとき、隣合うノ１ブア
ーム間に配設される第２圧縮はねはドライブプレート及
びノ１ブに対して直列に作用すると共に、第１圧縮ばね
と第２圧縮ばねとがドライブプレートを介して直列に作
用して、長い撓み範囲（振幅）をもって駆動力の変動ト
ルクを吸振減衰させる。When the driving member rotates, the driving arm of the driving member presses the first compression spring and is transmitted to the drive plate via the first compression spring. One end of the window in the plate presses against the second compression springs, compressing them and transmitting them to the knob 1 through these second compression springs. At this time, the second compression spring disposed between adjacent knob arms acts in series on the drive plate and the knob, and the first compression spring and the second compression spring are connected to each other through the drive plate. act in series to absorb and damp the fluctuating torque of the driving force over a long deflection range (amplitude).
実施例 以下、本発明の実施例を図面と共に詳述する。Example Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
第１図〜第２図は図外のフライホイール等の入力部材に
連結される駆動部材１と、図外の出力軸等の出力部材に
連結されるハブ２との間でトルクの伝達を行なう本発明
の一実施例を示す捩り振動減衰装置であり、駆動部材１
は、略環状を呈し、好ましくはハブ２及び後述する釣合
装置と同一の厚さをもって形成され、ハブ２よりも径方
向外方に離隔した位置にこのハブ２と同芯状に配設され
て、ハブ２と共に左右一対のドライブプレート３ａ。In Figures 1 and 2, torque is transmitted between a drive member 1 connected to an input member such as a flywheel (not shown) and a hub 2 connected to an output member such as an output shaft (not shown). It is a torsional vibration damping device showing one embodiment of the present invention, and the drive member 1
has a substantially annular shape, is preferably formed to have the same thickness as the hub 2 and the balancing device described later, and is arranged concentrically with the hub 2 at a position spaced radially outward from the hub 2. Along with the hub 2, there is a pair of left and right drive plates 3a.
３ｂ間に相対回動可能に挾持されている。この駆動部材
１は外周に図外の入力部材に噛合う係合突起４を円周方
向等間隔に備えると共に、内周に円周方向等間隔に突出
する複数個の駆動アーム５を備えており、この駆動アー
ム５，５間に第１圧縮ばね６が円周方向に隙間なく収容
、保持されている。そして、駆動部材１の左右のドライ
ブプレー）３ａ、３ｂには、駆動アーム５，５間の円周
方向長さと同一の円周方向長さの窓７が第１圧縮ばね６
に対応して形成され、この窓７が第１圧縮ばね６に円周
方向に隙間なく係合されている。一方、ハブ２は、出力
軸連結用の係止孔８が設けられたボス部９と、このボス
部９から径方向外方へ延出する環状部１０とから成り、
環状部１０の外周には円周方向等間隔に突出する４個の
ハブアームＵを形成しである。このハブアーム１１は、
径方向外方に広がる扇形状で、かつ、先端には両側から
円周方向に伸びるフィンガー１２を設けである。 １３
はハブアーム１１の外周位置で、かつ、左右のドライブ
プレート３ａ、３ｂ間に回動可能に配設された略環状の
釣合装置であり、この釣合装置１３はノ）ブアーム１１
と同一材料で同一の厚さをもって形成され、内周には隣
合うハブアーム１１ 、１１間に延出する釣合アーム１
４が円周方向等間隔にハブアーム１１と同数個突設され
ている。そして、この釣合アーム１４とハブアーム１１
との間に第２圧縮ばね１５が円周方向に隙間なく収容、
保持されていて、ハブ２の隣合うハブアーム１１ 、１
１間で直列に作用するばね群を形成しており、これらば
ね群の各々は並列に作用する。１６はハブ２の隣合うハ
ブアーム１１ 、１１間の円周方向長さと同一の円周方
向長さに形成されたドライブプレート３ａ、３ｂの窓で
あり、この窓１６に釣合アーム１４を介して直列に作用
する一対の第２圧縮はね１５ 、１５が係合されている
。１７は、左右のドライブプレー）３ａ、３ｂがハブ２
に外嵌された釣合装置１３と駆動部材１との間で屈曲形
成されて、リベット１８により接合固定された結合部で
あり、この結合部１７により駆動部材１の内周端と釣合
装置１３の外周端とが仕切られている。１９は一方のド
ライブプレート３ａとハブ２との間をシールするシール
装置である。3b so that they can rotate relative to each other. This drive member 1 is provided with engaging protrusions 4 on its outer periphery that engage with input members (not shown) at equal intervals in the circumferential direction, and is provided with a plurality of drive arms 5 that protrude at equal intervals in the circumferential direction on its inner periphery. A first compression spring 6 is accommodated and held between the drive arms 5, 5 without any gaps in the circumferential direction. In the left and right drive plates 3a and 3b of the drive member 1, a window 7 having the same circumferential length as the circumferential length between the drive arms 5 and 5 is provided with a first compression spring 6.
, and this window 7 is engaged with the first compression spring 6 without any gap in the circumferential direction. On the other hand, the hub 2 includes a boss portion 9 provided with a locking hole 8 for connecting the output shaft, and an annular portion 10 extending radially outward from the boss portion 9.
Four hub arms U are formed on the outer periphery of the annular portion 10 and project at equal intervals in the circumferential direction. This hub arm 11 is
It has a fan shape that expands outward in the radial direction, and is provided with fingers 12 extending in the circumferential direction from both sides at the tip. 13
is a substantially annular balancing device rotatably disposed at the outer peripheral position of the hub arm 11 and between the left and right drive plates 3a and 3b;
are made of the same material and have the same thickness, and on the inner periphery there is a counterbalancing arm 1 extending between adjacent hub arms 11, 11.
The same number of hub arms 4 as the hub arms 11 are protruded at equal intervals in the circumferential direction. And this balance arm 14 and hub arm 11
The second compression spring 15 is accommodated without any gap in the circumferential direction between the
The adjacent hub arms 11, 1 of the hub 2 are held
1 form a group of springs that act in series, and each of these spring groups acts in parallel. 16 is a window in the drive plates 3a, 3b formed to have the same circumferential length as the circumferential length between the adjacent hub arms 11, 11 of the hub 2; A pair of second compression springs 15, 15 acting in series are engaged. 17 is left and right drive play) 3a and 3b are hub 2
This is a joint that is bent and fixed between the balancing device 13 and the drive member 1, which are fitted onto the outside of the drive member 1, and is fixed by a rivet 18. 13 is partitioned off from the outer peripheral end. A sealing device 19 seals between one drive plate 3a and the hub 2.
以上の実施例構造によれば、駆動部材１に入力された駆
動力は、駆動部材１が回動することによって、駆動部材
１の駆動アーム５が第１圧縮ばね６を押圧し、この第１
圧縮ばね６に係合する窓７を介してドライブプレート３
ａ、３ｂに伝達され、次いで、ドライブプレート３ａ、
３ｂの窓１６の右端または左端が第２圧縮ばね１５ 、
１５を押圧してこれらを圧縮し、これら第２圧縮ばね１
５ 、１５を介してハブ２に伝達される。このとき、隣
合うハブアーム１１ 、１１間に配設される第２圧縮ば
ね１５ 、１５がドライブプレート３ａ ＃ ３ ｂ及
びノ１ブ２に対して釣合装置１３の釣合アーム１４を介
して直列に作用すると共に、第１圧縮ばね６と第２圧縮
ばね１５ 、１５とがドライブプレート３ａ、３ｂを介
して直列に作用することとなる。従って、このときの捩
り振動減衰装置の圧縮ばねの総合ばね定数には、第１圧
縮ばね６のばね定数をに、とし、第２圧縮ばね１５゜１
５のばね定数をそれぞれに２ａ ＊に２ ’ｂとすると
、１４−１／に、＋１ ／に２． ＋１／に２ｂとなり
、のってばね定数が小さく、その分大きい変位即ち長い
振幅をもった振動減衰装置が得られる。According to the structure of the embodiment described above, the driving force input to the driving member 1 is caused by the rotation of the driving member 1, which causes the driving arm 5 of the driving member 1 to press the first compression spring 6, and the driving force is applied to the first compression spring 6.
Drive plate 3 via window 7 engaging compression spring 6
a, 3b, and then the drive plates 3a,
The right end or left end of the window 16 of 3b is the second compression spring 15,
15 to compress these, and these second compression springs 1
5 and 15 to the hub 2. At this time, the second compression springs 15, 15 disposed between the adjacent hub arms 11, 11 are connected in series to the drive plates 3a #3b and the knob 2 via the balancing arm 14 of the balancing device 13. At the same time, the first compression spring 6 and the second compression springs 15 and 15 act in series via the drive plates 3a and 3b. Therefore, for the overall spring constant of the compression spring of the torsional vibration damping device at this time, the spring constant of the first compression spring 6 is set to , and the spring constant of the second compression spring 15°1
If the spring constants of 5 are respectively 2a* and 2'b, then 14-1/+1/2. +1/2b, which results in a vibration damping device with a small spring constant and a correspondingly large displacement, that is, a long amplitude.
また、駆動部材１及び釣合装置１３を、ノ）ブアーム１
１の外周ｌこ、該ハブアーム１１と同一の肉厚をもって
形成することにより、ハブ２と駆動部材１及び釣合装置
１３を、同一金属板材料から打抜き形成することが可能
で、ハブ２と駆動部材１及び釣合装置１３を別材料で形
成する場合に較べて、材料の無駄がなく、製作コストを
下げることができると共に、前記釣合装置１３の釣合ア
ーム１４は、通常、ハブアーム１１の厚さの１／２の位
置に軸心を一致させて配設される圧縮ばね１５ 、１５
のばね力を、これら圧縮ばね１５ 、１５の略軸心位置
で受けることができる。In addition, the driving member 1 and the balancing device 13 are
By forming the outer periphery of the hub arm 1 with the same wall thickness as the hub arm 11, the hub 2, the driving member 1, and the balancing device 13 can be formed by stamping from the same metal plate material, and the hub 2 and the driving member 1 can be formed by stamping from the same metal plate material. Compared to the case where the member 1 and the balancing device 13 are made of different materials, there is no waste of material and manufacturing costs can be reduced. Compression springs 15, 15 arranged with their axes aligned at 1/2 the thickness
The spring force can be received at approximately the axial center position of these compression springs 15, 15.
尚、本実施例においては、第１圧縮はね６として内外二
重の入れ子形ばねを採用しているが、これに限られるも
のでなく、適宜な圧縮ばねを選択して使用できることは
もちろんである。又、第２圧縮ばね１５ 、１５を４組
円周方向に配設する態様を示したが、これに限られるも
のでなく、適宜の組数の第２圧縮はね１５ 、１５を配
設する態様としてもよい。In this embodiment, a double inner and outer nested spring is used as the first compression spring 6, but the invention is not limited to this, and it is of course possible to select and use an appropriate compression spring. be. Further, although four sets of the second compression springs 15 , 15 are arranged in the circumferential direction, the embodiment is not limited to this, and an appropriate number of sets of the second compression springs 15 , 15 may be arranged. It may also be a mode.
発明の効果
以上のように本発明によれば、略環状の駆動部材をハブ
の径方向外方の離隔した位置に配設し、この駆動部材の
駆動アーム間に収容、保持される第１圧縮ばねと、ハブ
のハブアームとハブアームに回動可能に外嵌された釣合
装置の釣合アームとの間に収容、保持されて、釣合アー
ムを介して直列に作用する第２圧縮ばねとが、ドライブ
プレートを介して直列に作用するように成されているた
め、従来得ることができなかった長い撓み振幅を得るこ
とができる。Effects of the Invention As described above, according to the present invention, a substantially annular drive member is disposed at a spaced apart position radially outward of the hub, and the first compression member is housed and held between the drive arms of the drive member. a second compression spring housed and held between the hub arm of the hub and a counterbalancing arm of a counterbalancing device rotatably fitted onto the hub arm and acting in series via the counterbalancing arm; , so that they act in series through the drive plate, making it possible to obtain a long deflection amplitude that could not be obtained conventionally.
第１図は本発明の一実施例を示す捩り振動減衰装置の正
面図、第２図は第１図における■−■線断面図、第３図
は従来例を示す正面図、第４図は第３図のＩＶ−ＩＶ線
断面図である。
１・・・駆動部材、２・・・ハブ、３ａｍ３ｂ・・・ド
ライブプレート、５・・・駆動アーム、６・・・第１圧
縮ばね、７・・・窓、１１・・・ハブアーム、１３・・
・釣合装置、１４・・・釣合アーム、１５・・・第２圧
縮ばね、１６・・・窓。
第２図
第４図Fig. 1 is a front view of a torsional vibration damping device showing an embodiment of the present invention, Fig. 2 is a sectional view taken along the line ■-■ in Fig. 1, Fig. 3 is a front view showing a conventional example, and Fig. 4 is a front view of a torsional vibration damping device showing an embodiment of the present invention. 4 is a sectional view taken along the line IV-IV in FIG. 3. FIG. DESCRIPTION OF SYMBOLS 1... Drive member, 2... Hub, 3am3b... Drive plate, 5... Drive arm, 6... First compression spring, 7... Window, 11... Hub arm, 13...・
- Balance device, 14... Balance arm, 15... Second compression spring, 16... Window. Figure 2 Figure 4
Claims (1)
されるハブとの間でトルクの伝達を行なう捩り振動減衰
装置であつて、前記駆動部材は略環状で、前記ハブより
も径方向外方の離隔した位置にこのハブと同芯状に配置
されて前記ハブと共に左右一対のドライブプレート間に
相対回動可能に挾持され、かつ、この駆動部材は内周に
円周方向等間隔に突出する複数個の駆動アームを備え、
該駆動アーム間に第１圧縮ばねが円周方向に収容、保持
されていて、この第１圧縮ばねに前記ドライブプレート
がこれに形成した窓をもつて係合する一方、前記ハブは
外周に円周方向等間隔に突出する複数個のハブアームを
有し、該ハブアームの外周には、内周に前記ハブの隣合
うハブアーム間に延出する釣合アームを円周方向等間隔
に突設した略環状の釣合装置が回動可能に外嵌され、こ
の釣合アームと前記ハブアームとの間に第２圧縮ばねが
円周方向に収容、保持されて、前記ハブの隣合うハブア
ーム間で直列に作用するばね群を形成し、前記ドライブ
プレートが前記ハブの隣合うハブアーム間の円周方向長
さと同一の円周方向長さの窓をもつて前記第２圧縮ばね
に係合されてなることを特徴とする捩り振動減衰装置。(1) A torsional vibration damping device that transmits torque between a drive member connected to an input member and a hub connected to an output member, wherein the drive member has a substantially annular shape and is more radial than the hub. The drive members are disposed concentrically with the hub at a spaced apart position on the outside and are relatively rotatably sandwiched together with the hub between a pair of left and right drive plates, and the drive members are arranged on the inner periphery at equal intervals in the circumferential direction. Equipped with multiple protruding drive arms,
A first compression spring is circumferentially received and retained between the drive arms, and the drive plate engages the first compression spring with a window formed therein, while the hub is circumferentially circumferentially engaged. It has a plurality of hub arms protruding at equal intervals in the circumferential direction, and on the outer periphery of the hub arms, balancing arms extending between adjacent hub arms of the hub are protruded at equal intervals in the circumferential direction on the inner periphery. An annular counterbalancing device is rotatably fitted over the counterbalancing arm, and a second compression spring is circumferentially housed and retained between the counterbalancing arm and the hub arm, the second compression spring being arranged in series between adjacent hub arms of the hub. forming a group of operative springs, the drive plate being engaged by the second compression spring with a window of circumferential length equal to the circumferential length between adjacent hub arms of the hub; Features a torsional vibration damping device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24606886A JPS63101537A (en) | 1986-10-16 | 1986-10-16 | Torsional vibration damping device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24606886A JPS63101537A (en) | 1986-10-16 | 1986-10-16 | Torsional vibration damping device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63101537A true JPS63101537A (en) | 1988-05-06 |
Family
ID=17142986
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24606886A Pending JPS63101537A (en) | 1986-10-16 | 1986-10-16 | Torsional vibration damping device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63101537A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1989012768A1 (en) * | 1988-06-24 | 1989-12-28 | Kabushiki Kaisha Daikin Seisakusho | Damper disc |
| US5289737A (en) * | 1990-08-25 | 1994-03-01 | J. M. Voith Gmbh | Elastic clutch |
| WO2009068453A3 (en) * | 2007-11-29 | 2010-01-07 | Zf Friedrichshafen Ag | Hydrodynamic coupler |
| FR2940825A1 (en) * | 2009-01-08 | 2010-07-09 | Valeo Embrayages | DOUBLE FLYWHEEL DAMPER WITH DOUBLE DAMPING MEANS, IN PARTICULAR FOR A MOTOR VEHICLE |
| JP2011179557A (en) * | 2010-02-26 | 2011-09-15 | Aisin Aw Industries Co Ltd | Damper device |
-
1986
- 1986-10-16 JP JP24606886A patent/JPS63101537A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1989012768A1 (en) * | 1988-06-24 | 1989-12-28 | Kabushiki Kaisha Daikin Seisakusho | Damper disc |
| US5149303A (en) * | 1988-06-24 | 1992-09-22 | Kabushiki Kaisha Daikin Seisakusho | Clutch damper disc assembly |
| US5289737A (en) * | 1990-08-25 | 1994-03-01 | J. M. Voith Gmbh | Elastic clutch |
| WO2009068453A3 (en) * | 2007-11-29 | 2010-01-07 | Zf Friedrichshafen Ag | Hydrodynamic coupler |
| FR2940825A1 (en) * | 2009-01-08 | 2010-07-09 | Valeo Embrayages | DOUBLE FLYWHEEL DAMPER WITH DOUBLE DAMPING MEANS, IN PARTICULAR FOR A MOTOR VEHICLE |
| WO2010079273A1 (en) * | 2009-01-08 | 2010-07-15 | Valeo Embrayages | Double damping flywheel with double damping means, notably for a motor vehicle |
| CN102272473A (en) * | 2009-01-08 | 2011-12-07 | Valeo离合器公司 | Double damping flywheel with double damping means, notably for a motor vehicle |
| US8690688B2 (en) | 2009-01-08 | 2014-04-08 | Valeo Embratages | Double damping flywheel with double damping elements |
| JP2011179557A (en) * | 2010-02-26 | 2011-09-15 | Aisin Aw Industries Co Ltd | Damper device |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6585091B2 (en) | Torsional vibration damper | |
| US4669595A (en) | Clutch disc for a motor vehicle friction clutch | |
| CN108138898B (en) | Torsional vibration damper for a hydrodynamic torque coupling | |
| JPH0228747B2 (en) | ||
| US5176233A (en) | Apparatus for reducing vehicle drive train vibrations | |
| US4573945A (en) | Damper disc of a long travel type | |
| US5697846A (en) | Damper disc assembly | |
| US5401213A (en) | Clutch and damper assembly | |
| US5059155A (en) | Friction device of damper disc | |
| JPS63101537A (en) | Torsional vibration damping device | |
| JP3669664B2 (en) | Flywheel assembly | |
| JPH0577889B2 (en) | ||
| JPH0332832Y2 (en) | ||
| JP2022030692A (en) | Damper device | |
| US20070099710A1 (en) | Flexible flywheel | |
| JPH11182576A (en) | Stop pin, and damper disk assembly | |
| JPH0155690B2 (en) | ||
| JPH0577890B2 (en) | ||
| US20230258242A1 (en) | Torsional vibration reducing device | |
| JP2002310185A (en) | Clutch disc assembly | |
| JP2607354Y2 (en) | Flywheel assembly | |
| JPH0577891B2 (en) | ||
| JP3408660B2 (en) | Damper mechanism | |
| JPH053774Y2 (en) | ||
| JP2602895Y2 (en) | Torsional vibration reduction device |