JPS5934024A - Torsional vibration damper - Google Patents
Torsional vibration damperInfo
- Publication number
- JPS5934024A JPS5934024A JP13452783A JP13452783A JPS5934024A JP S5934024 A JPS5934024 A JP S5934024A JP 13452783 A JP13452783 A JP 13452783A JP 13452783 A JP13452783 A JP 13452783A JP S5934024 A JPS5934024 A JP S5934024A
- Authority
- JP
- Japan
- Prior art keywords
- disk
- disc
- damping
- torsional vibration
- vibration damper
- 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
- F16F15/12—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
- F16F15/129—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 characterised by friction-damping means
-
- 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
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/14—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions combined with a friction coupling for damping vibration or absorbing shock
-
- 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)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本発明は軸方向にかつ回転不能に互いに結合されたカバ
ー円板の間に受容された駆動円板と被駆動円板とを有し
、この駆動円板と被駆動円板とが周方向に互いに相対的
にかつそれぞれカバー円板に対して運動可能でかつカバ
ー円板に対して周方向に互いに無関係に、力・ぐ−円板
と駆動円板若しくは被、駆動円板とに周方向に分配され
て設けられた周方向切欠き内に受容された周方向に作用
する減衰ばねから成るそれぞれ１つの減衰ばね群を介し
て支えられているねじれ振動減衰器に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention includes a drive disc and a driven disc received between cover discs that are axially and non-rotatably coupled to each other. are movable relative to each other in the circumferential direction and each with respect to the cover disk, and independently of each other in the circumferential direction with respect to the cover disk, the force/force disk and the drive disk or the drive disk. The present invention relates to a torsional vibration damper which is supported via a respective damping spring group of circumferentially acting damping springs received in circumferential recesses distributed circumferentially between the torsional vibration dampers.
速機を有する自動車用駆動装置に於てトルクコン・Ｓ−
夕又は流体クラッチと関連して用いられ、発生ずる不等
速性、衝撃負荷及びそれに類似したものを補償しかつね
じれ振動をその発生時点から回避するために役立つ。Torque converter/S- in automotive drive systems with speed gears
It is used in conjunction with hydraulic clutches or hydraulic clutches to compensate for occurring inconsistencies, shock loads and the like and to avoid torsional vibrations from the moment they occur.
トルクコン・ぐ−夕を有する自動車用駆動装置に用いら
れる２段式ねじれ振動減衰器は西１・ゝイッ国特許出願
公開第３０４７０３９号明細書に記載されている。この
場合にはトルクコンバータによって駆動された駆動円板
と被駆動軸と回転不能に結合された被駆動円板とは力・
ζ−円板の間に受容され、これに対して周方向に作用す
る減衰ばねによって支えられている。この場合には駆動
円板とカバー円板との間とカバー円板と被、駆動円板と
の間では、各段に於て互いに直列に接続された複数の減
衰ばわから成る周方向に分配された複数のばね群が存在
していることにより比較的に大きな相対運動が実現され
る。A two-stage torsional vibration damper for use in a motor vehicle drive system having a torque converter is described in US Pat. No. 3,047,039. In this case, the driving disk driven by the torque converter and the driven disk non-rotatably coupled to the driven shaft are
ζ - supported by a damping spring received between the discs and acting circumferentially thereon. In this case, between the drive disc and the cover disc, and between the cover disc and the cover disc, the damping disc is distributed in the circumferential direction, consisting of a plurality of damping discs connected in series to each other in each stage. A relatively large relative movement is achieved by the presence of a plurality of spring groups.
この場合には各ばね群の周方向切欠きに受容された減衰
ばねの間には半径方向に向けられたｊ車行体が配置され
ている。この連行体（ま−ノ５の段では部分的には駆動
円板と結合され力・つ名し公的には駆動円板を間に受容
する力・ぐ−円板と結合され、他方の段では周方向に移
動可能に支承され、駆動円板から被駆動円板への回動ト
ルりの伝達とこれらの円板と力・ζ−円板との間の減衰
された相対運動、ひいては駆動円板と被駆動円板との間
の相対運動を可能にする。In this case, a radially oriented j-wheel body is arranged between the damping springs which are received in the circumferential recess of each spring group. This driving body (in the 5th stage, it is partially connected to the drive disk, and officially known as the force force that receives the drive disk between them). The stages are supported so as to be movable in the circumferential direction and are capable of transmitting the rotational torque from the driving disc to the driven disc and the damped relative movement between these discs and the force/ζ disc, and thus Allows relative movement between the driving and driven discs.
本発明の目的は構造が簡単であって、しかもねじれ振動
の周期的な励起を効果的に抑えることのできる振動減衰
器を提供することで・ある。An object of the present invention is to provide a vibration damper which has a simple structure and can effectively suppress periodic excitation of torsional vibration.
この目的は本発明によれば冒頭に述べた形式のねじれ振
動減衰器に於て、駆動円板と力・り一円板との間と力・
ζ−円板と被駆動円板とのｆｔ、とにこれらの円板の間
に相対運動が生じた場合に有効である摩擦段がそれぞれ
１つ設けられて℃・イ）ことによって達成された。This object, according to the invention, is to provide a torsional vibration damper of the type mentioned at the outset, between the drive disk and the force/force disk.
This was achieved by providing one friction stage in each of the ζ-disk and the driven disk, respectively, which is effective when relative motion occurs between these disks.
すなわち本発明の構成によっては減衰ばねに、ｌ：り行
なわれる振動減衰作用に摩擦段犀トつて与えられる減衰
効果が重畳され、振動励起力が迅速に減衰され、ひいて
はねじれ振動が発生時点で抑えられることになる。In other words, depending on the configuration of the present invention, the damping effect provided by the friction stage is superimposed on the vibration damping effect performed by the damping spring, and the vibration excitation force is quickly damped, and as a result, torsional vibration is suppressed at the moment it occurs. It will be done.
本発明の１実施例によれば各減衰ばね群の減衰ばねが互
いに並列的に接続されているのに対し、両方の減衰ばね
群が互いに直列的に接続されており、駆動円板と被駆動
円板との間に回動角度が生じた場合に、この両方の円板
に配属された減衰ばね群が協働するようになっている。According to one embodiment of the invention, the damping springs of each damping spring group are connected in parallel with each other, whereas both damping spring groups are connected in series with each other, so that the drive disk and the driven When a rotation angle occurs between the two discs, the damping spring groups assigned to both discs cooperate with each other.
直列に接続されている場合には合成ばね特性線は並列的
に接続された単個ばねの特性線よりも平らな経過を有し
ているので、このような形式では回動トルクが小さい場
合にも著しい回動角度を生せしめることができる。この
場合には各減衰ばね群の減衰ばねは互いに同じばね硬さ
を有していると有利である。これに対して異なる減衰ば
ね群の減衰ばねは互いに異なるばね硬さを有している。When connected in series, the composite spring characteristic line has a flatter course than the characteristic line of single springs connected in parallel, so in this type of configuration, when the turning torque is small, It is also possible to produce a significant rotation angle. In this case, it is advantageous if the damping springs of each damping spring group have the same spring stiffness. On the other hand, the damping springs of different damping spring groups have different spring stiffnesses.
個々の減衰ばね群の減衰ばねの実現可能なばね行程とば
ね硬さを適当に設計することによつて、駆動円板と被駆
動円板どの間の所定の回動角度からは初期範囲とは異っ
た特性線経過を与えることができる。これは、異なる減
衰ば−ね群の減衰ばねの協働が所定の回動角度に達した
後で解消さ゛せられること訛よって達成される。１異な
る減衰ばね群の、初期回動角度範囲に於て直列的に接続
されて作用する減衰ばねの協働は、一方の減衰ばね群の
減衰ばねが所定の回動角度範囲（（達した後で完全に緊
縮され、他方の減衰ばね群の減衰ばねだけが所属の円板
と力・ぐ−円板との間、ひいては被駆動円板と駆動円板
との間で相対運動を許さなくなるので解消される。By appropriately designing the achievable spring travel and spring stiffness of the damping springs of each damping spring group, it is possible to determine the initial range from a given rotation angle between the driving disc and the driven disc. Different characteristic curves can be provided. This is achieved in that the cooperation of the damping springs of the different damping spring groups is released after reaching a predetermined rotation angle. 1. The cooperation of the damping springs of different damping spring groups, which are connected in series and act in the initial rotation angle range, is such that the damping springs of one damping spring group reach a predetermined rotation angle range (((after reaching is completely tightened, and only the damping springs of the other damping spring group do not permit relative movement between the associated disk and the force disk, and therefore between the driven disk and the driving disk. It will be resolved.
一方の減衰ばね群の減衰ばねがこの第２０回動角１度範
囲の前でブロックされると回動にまだ関与する減衰ばね
の特性線しか有効でな（なることは言うまでもない。本
発明の別の実施例によれば力・々−内円板対する駆動円
板及び（又は）被駆動円板の相対運動性が、周方向に作
用するストン・ξによって所定の回動角度に制限されて
おり、これによってこのストン・ξが作用するようにな
ると、当該の回転方向で・所属の円板とカバー円板との
間に回動不能な結合が生じ、これらの円板の間で作用す
る減衰ばねが遮断される。If the damping springs of one damping spring group are blocked before the 20th rotation angle range of 1 degree, only the characteristic line of the damping springs that are still involved in rotation will be valid (it goes without saying that this will become the case). According to another embodiment, the relative movement of the drive and/or driven disk with respect to the inner disk is limited to a predetermined rotation angle by a circumferentially acting cylinder ξ. When this stone ξ comes into action, a non-rotatable connection occurs between the associated disc and the cover disc in the relevant direction of rotation, and the damping spring acting between these discs is blocked.
これに対して本発明の別の１実施例に於ては少な（とも
一方の減衰ばね群の減衰ばねにプレロー１５がかげられ
ている。この場合には次第に減少する特性線経過が得も
ねる。一方の減衰ばね群のプレロードがかけられていな
いか又は弱いプレロー＋ｙ Ｌかかけられていない減衰
ばねは初期回動角度範囲に於てはさしあたり単独で作用
し、回動トルク経過を固有のばね硬さに応じて発生する
回動角度に関連して決定する。この減衰ばね群の減衰ば
ねのばね力が緊縮に基づいて他方の減衰ばね群の減衰ば
ねのプレロードカに達すると、両方の減衰ばね群の減衰
ばねが並列的に接続されて作用し、達成可能な回動角度
は個々の減衰ばね群に於て生じる回動角度の和として与
えられる。回動角度に関連した回動ｌ、ルクの特性線は
より平らな経過を有することになり、両方の減衰ばね群
の減衰ばねが協働する回動角度範囲に於ける全体の特性
線Ｏま、汀ジｌのＭ ｉばね群のプレロードのかげられ
て（・なし・減衰ばねだけしか作用しない初期回動角度
範囲にｊｉ交べて次第に減少する経過を有するようにな
る。On the other hand, in a further embodiment of the invention, the damping springs of one of the damping spring groups are provided with a pre-lowering 15. In this case, a gradually decreasing characteristic line profile is not advantageous. .One of the damping spring groups is not preloaded or is weakly preloaded.The damping spring that is not preloaded with L is acting alone for the time being in the initial rotational angle range, and the course of rotational torque is determined by the characteristic spring. Determined in relation to the rotation angle that occurs depending on the stiffness.When the spring force of the damping spring of this damping spring group reaches the preload force of the damping spring of the other damping spring group due to tightening, both damping springs The damping springs of the groups are connected in parallel and act, and the achievable pivoting angle is given as the sum of the pivoting angles occurring in the individual damping spring groups. The characteristic line of will have a flatter course, and the overall characteristic line O, in the range of rotational angles in which the damping springs of both damping spring groups cooperate, will have a flatter course. The rotation angle gradually decreases after reaching the initial rotation angle range in which only the damping spring acts.
゛本発明の別の実施例に於ては第３の減衰※了ね群が設
けられている。この場合には第３の減衰ばね群は駆動円
板とカッζ−円板との間若しくをまカバー円板と被駆動
円板との間に所定の回動角度が得られた後で有効になる
ように構成されているので、こ才１らの付加的な減衰ば
ねＯま所定の回動角度に達した後でまだ有効である減衰
Ｑ了」〕群に並列的に接続される。この結果、面１回動
性が著しく高められ、回動角度に関連した回動トルク特
性線の勾配の大きい経過をもたらす。この場合には、所
定の回動角度に達したあとで（まじめて有効になる減衰
ばね群の減衰ばね番主力・ぐ−円板と回動不能に結合さ
れ、駆動円板若しくは被駆動円板に設けられた、この減
衰ばね群の減衰ばわの長さを周方向で所定の長さだけ両
側に越える円弧状の切欠き内に受容されていると有利で
・ある。減衰ばねがばねの長さを周方向で両側に越える
周方向切欠きに受容されていることによって、前記減衰
ばねはその端面と円弧状の切欠きを周方向に制限する縁
との間の空間を進んだあとではじめて前記切欠きの縁に
当接する。この縁は減衰ばねのストン・Ｑとして作用し
、この減衰ばねはまだ有効である減衰ばね群の減衰ばね
に対して並列的に接続される。In another embodiment of the invention, a third attenuation group is provided. In this case, the third damping spring group is activated after a predetermined rotation angle is obtained between the drive disc and the cover disc or between the cover disc and the driven disc. The additional damping springs 0 and 1 are connected in parallel to the damping springs 1 and 2 which are configured to be effective and are still effective after reaching a predetermined rotation angle. . As a result, the one-plane rotational properties are significantly increased, resulting in a highly sloped course of the rotational torque characteristic line as a function of the rotational angle. In this case, after reaching a predetermined rotation angle (the main force of the damping spring group becomes effective), the main force of the damping spring group becomes unrotatably connected to the disk, and the drive disk or driven disk Advantageously, the damping springs are accommodated in arc-shaped recesses which extend on both sides by a predetermined length in the circumferential direction and extend the length of the damping ribs of this damping spring group. By being received in a circumferential notch extending over its length in the circumferential direction, the damping spring can, after having traveled through the space between its end face and the edge circumferentially limiting the arcuate notch. For the first time, it abuts the edge of the recess, which acts as a spring Q of the damping spring, which is connected in parallel to the damping spring of the damping spring group that is still active.
本発明の別の１実施例によれば、駆動円板とカバー円板
との間及び（又は）力・ンー円板と被駆動円板との間に
、所定の回動角度に達した後ではじめて有効になる負荷
摩擦段が設けられている。この負荷摩擦段はばね負荷さ
れた、周方向で互いに相対的に運動可能な円板の間に制
限されて軸方向に運動可能にかつ前記円板の一方、に対
して所定の角度だけ摩擦なしに回転可能に支承された摩
擦円板を有している。この場合には摩擦なしで回転可能
な範囲を連行された後で摩擦円板は前述の円板の一方、
例えば被駆動＝Ｐ板と回動不能に結合される。According to a further embodiment of the invention, after a predetermined rotational angle is reached between the driving disc and the cover disc and/or between the force disc and the driven disc. A load friction stage is provided that becomes effective only when the This loaded friction stage is confined between spring-loaded discs movable relative to each other in the circumferential direction and movable in the axial direction and rotates without friction through a predetermined angle relative to one of said discs. It has a removably mounted friction disc. In this case, after being carried through the range in which it can rotate without friction, the friction disk is one of the aforementioned disks,
For example, it is unrotatably coupled to the driven = P plate.
さらに本発明の別の実施例によれば、駆動円板と被駆動
円板との間で直接的に作用する摩擦段が設けられており
、相対回動が生じた場合に駆動円板と力・ζ−円板との
間とカバー円板と被駆動円板との間の摩擦作用に加えて
駆動円板と被駆動円板との間に直接的な摩擦が生ぜしぬ
られろようになっている。Furthermore, according to a further embodiment of the invention, a friction stage is provided which acts directly between the driving disc and the driven disc, so that in the event of a relative rotation, the driving disc and the force・ζ - In addition to the friction between the disk and the cover disk and the driven disk, direct friction is generated between the driving disk and the driven disk. It has become.
又、本発明によるねじれ振動減衰器の１実施例に於ては
各摩擦段に、周方向に互いに相対的に運動可能な円板の
一方の摩擦面に圧着された少な（とも１つの摩擦リング
が設けられている。In one embodiment of the torsional vibration damper according to the invention, each friction stage has at least one friction ring crimped onto one friction surface of the disks movable relative to each other in the circumferential direction. is provided.
少な（とも１つの摩擦段に於てはこの摩擦リングは制限
されて軸方向に運動可能に支承された抑圧円板によって
、周方向に互いに相対的に運動可能な円板の一方の摩擦
面に圧着されているのに対し、抑圧板はばね力で負荷さ
れてこの摩擦段に於て協働する他方の円板に回動不能に
支承されている。抑圧円板若しくは摩擦リングを圧着す
るためにはそれぞれ１つの皿ばねを用いることができる
。In one friction stage, this friction ring is limited by means of a restraining disk which is supported so as to be movable in the axial direction, and on one of the friction surfaces of the disks which are movable relative to each other in the circumferential direction. In contrast, the suppression plate is spring-loaded and is supported non-rotatably on the other cooperating disc in this friction stage.For crimping the suppression disc or friction ring. One Belleville spring can be used for each.
次に図面について本発明を説明する：
第１図と第２図に図示された全体として符と・１０で示
されたねじれ振動減衰器は一点瑣線で示されている駆動
部分１１と駆動円板１２を介して相対回転不能に駆動結
合されている。駆動円板１２はＵいに軸方向の間隔をお
いて配置斤された、Ｕいに回転不能にかっ１１ζ１１方
向に移動不能に結合された力、％＋−円板１３．１４の
間に受容されている。力・ぐ−円板相が間の結合を行な
うためにはカバー円板とりベラ“トｄ−めされたスペー
サビン１５が用いられている。このス（−サピン１５は
力・ζ−円板の外縁の近くに周方向に分配されて配置さ
れており、駆動円板に設けられた円弧状の長孔１６を貫
いている。この長孔１６の周方向の長さの範囲内でスペ
ーサピン１５は運動することができ、延いては力・ζ−
円板１３．１４と駆動円板１２とが互いにＦＩＴ対的に
回動することができる。The invention will now be explained with reference to the drawings: The torsional vibration damper illustrated in FIGS. They are drive-coupled through a plate 12 so as to be non-rotatable relative to each other. The drive disks 12 receive force between the disks 13.14, which are non-rotatably coupled to the drive disks 12 and are axially spaced apart. has been done. A spacer pin 15, which is fitted with a cover disc and a bellows, is used to make the connection between the force and the disc phase. The spacer pins 15 are arranged near the outer edge and distributed in the circumferential direction, and pass through an arc-shaped long hole 16 provided in the drive disk. can move, and in turn the force ζ−
The discs 13, 14 and the drive disc 12 can be rotated relative to each other.
スペーサピン１５が貫く長孔１６に対して周方向にずら
され、周方向に分配されて配置された、力・ミー円板１
３，１４と駆動円板１２とに設けられた４ｊ：いりこ整
合する周方向切欠さ１７゜１８、ＩｃＩに減αばね２０
が受容されている。A force/me disk 1 is shifted in the circumferential direction with respect to the elongated hole 16 through which the spacer pin 15 passes, and is distributed in the circumferential direction.
3, 14 and drive disk 12: circumferential notch 17°18 for alignment, α spring 20 reduced to IcI
is accepted.
この減衰ばね２０によって駆動円板１２と力・Ｓ−ｌ［
ｌ 、ｆ！）］、 ３ 、１４−とが１．’、Ｊ方向で
痒いに支えられる。ｌ１ｌｋ Ａばね２０は、カバー円
板に於ける周方向切欠き１７．１８の外側の縁部がそれ
ぞれ外側に向かつて曲げられ、減衰ばねが少なくとも部
・公的に−にから關まれることによって駆動円板１２と
力・ζ−円板１３．１４の窓状の周方向切欠きに保持さ
れる。力、に哀ばね２０の半径方向内側には、（駆動円
板の両側に輩擦リング２２ 、２３が配置されている。This damping spring 20 causes the drive disk 12 and the force S-l [
l, f! )], 3, 14- and 1. ', supported by itching in the J direction. l1lk A spring 20 is produced by bending the outer edges of the circumferential recesses 17, 18 in the cover disk towards the outside in each case, so that the damping spring is at least partially clamped from the It is held in a window-like circumferential cutout in the drive disk 12 and the force/ζ disk 13.14. Radially inside the force spring 20, friction rings 22, 23 are arranged (on both sides of the drive disk).
これらの摩擦リングは一第１の１屑擦段を形成する他に
、周方向に分配されて配置？′ｔされた減ヴばね２０と
協働して第１の減Ｑ段を形成する。摩擦リング２３は内
側のカバー円板］４の内側の摩擦面と直接的に協（ト）
するのに対し、ｆ屯、ｊｙの摩擦リング２２はカバー円
板１３．１４と回転不能ではあるかしがし制限されて軸
方向に運動可能に結合された押圧円板２４を介して、外
側の力・ζ−円板１３に支えられた皿はね２５によって
１駆動円板に圧着されている。These friction rings, in addition to forming the first scraping stage, are also distributed in the circumferential direction. The first Q-reducing stage is formed in cooperation with the Q-reducing spring 20. The friction ring 23 cooperates directly with the inner friction surface of the inner cover disc]4.
On the other hand, the friction rings 22 of fton, jy are connected to the cover disk 13.14 by means of a pressure disk 24 which is non-rotatably but limitedly movable in the axial direction. The force of ζ - The countersunk supported by the disc 13 is pressed against the drive disc 1 by the spring 25.
押圧円板２４は力・ぐ−円板を軸方向にがっ回動Ｔ”
ａ Ｃ（−’５いに結合するスペーサピン１５のＩＧ
囲に第１図に示すようにスペーサビン１５を部分的に−
１−から掴む、半径方向外方に延びる区分２６を有して
いる。The pressing disk 24 rotates the force disk in the axial direction T''
a C(-'5 IG of spacer pin 15 connected to
As shown in FIG.
It has a radially outwardly extending section 26 which is gripped from 1-.
駆動円板１２の半径）ｊ向内方にはこれに対して同軸的
に力・ミー円板１３．１４−の間に被駆動円板３０が受
容されている。この被駆動円板３０は設ス側で内歯３２
を介して第２図に於て１点鎖線で示された被駆動１１＃
ｌ＋ ３４の対応する外歯３３と回転不能に結合されて
いる。力・ζ−円板１３．１４と被駆動円板３ｏとに設
けられた、周方向に分配されて配置された、〃いに整合
する周方向切欠き３６，３７．３８内には同様に周方向
に作用する減衰ばね４ｏが受容されており、力・ぐ−円
板に設けられまた周方向切欠きの外側の縁を外へ曲げる
ことによって保持されている。この内側の減衰ばね４０
によっては被駆動円板３０と力・ζ−円阪１３．１４と
が周方向（こ弾性的に相醸に支えられている。駆動円板
の場合のように彼１駆動円板のゼス側の隊の・範囲には
被駆動円板の両側に摩擦リング４２．４３が配置されて
いる。摩擦リング４２が破、ニル動円阪と前方のカバー
円板１３の対応するＮ環筒との間で直接的に作／Ｔ７
しているの２こ対し、摩擦リング４３は制限されて・ｆ
！＋ 、１５向に運動可能に案内さねかつ力・ζ−円阪
と回転不能に結りされた押圧円板４４を介して被駆動円
板３０の池方の側に圧着されている。圧着力は後で第３
減衰段との関係で詳述する負荷摩擦円板４８に支えられ
た皿ばね４５によって与ｊえられる。A driven disk 30 is received coaxially inwardly of the drive disk 12 in the radius )j between force and force disks 13, 14-. This driven disk 30 has internal teeth 32 on the installation side.
Driven 11# indicated by a dashed line in FIG.
It is non-rotatably connected to the corresponding external tooth 33 of l+ 34. Similarly, in the circumferential notches 36, 37, 38 provided in the force/ζ disk 13.14 and the driven disk 3o, distributed in the circumferential direction and aligned with A damping spring 4o acting in the circumferential direction is received and is mounted on the force disk and held by bending out the outer edge of the circumferential recess. This inner damping spring 40
In some cases, the driven disk 30 and the force ζ - Ensaka 13.14 are mutually supported in the circumferential direction (this elastically. Friction rings 42 and 43 are placed on both sides of the driven disc in the area of the unit.The friction rings 42 are broken, and the N ring cylinder corresponding to the front cover disc 13 is connected to the friction ring 42. Created directly between / T7
In contrast, the friction ring 43 is limited.
! It is crimped to the side of the driven disk 30 via a pressing disk 44 which is non-rotatably connected to the guide tongue and force/ζ-Ensaka so as to be movable in + and 15 directions. The crimping force will be adjusted later.
It is provided by a disk spring 45 supported by a load friction disk 48, which will be explained in more detail in relation to the damping stage.
負荷摩擦円板４８は被駆動円板３０に対して同軸的にか
つ被駆動円板と内側の力・ζ−円ｉ１手との間に軸方向
に運動可能に配置されている。A load friction disk 48 is arranged coaxially with respect to the driven disk 30 and movable in the axial direction between the driven disk and the inner force ζ-circle i1.
被駆動円板３０とカバー円板１３．１４とに設けられた
、第２の減衰段の減衰ばね４０を受容する周方向切欠き
の範囲に於ては、負荷摩擦円板４８に同様に周方向切欠
き４９が設けられている。しかしこの周方向切欠きの周
方向の寸法は被駆動円板と力・Ｓ−円板とに設けられた
周方向切欠きよりも大きいので、負荷摩擦円板は減衰ば
わ４０が周方向切欠き４９の円方向制限面に当接するこ
となしに前述の円板に対して所定の周方向の運動性を有
している。この負荷摩擦円板４８は２つの減衰ばね５０
と協働して第３の減食段を形成する。この両方の減衰ば
ね５０はげいに対称的にそれぞれ第２の減衰段の複数の
減食ばね４０の間で力・ζ−円板１３．１４に於けるｊ
１厄のり方向切欠き５１．５２に受容されており、被駆
動円板３０と負荷摩擦円板４８とＧこ於けるそれぞれ整
合する周方向切欠き５３゜５４を貫いている。被駆動円
板３０と負荷摩擦円板４８とに於ける周方向切欠き５３
．５４は周方向に減衰ばね５０の周方向の寸法を越えて
延びているので、減衰ばね５０は被駆動円板３０が力・
Ｓ−円板１３．１４に対して所定量の回動をした後では
じめて被駆動円板に於ける周方向切欠き５３の周方向の
制限面に当接し、延いてはＡ７７述の所定の回動角度が
生じた後ではじめて有効になる。In the area of the circumferential recess in the driven disk 30 and the cover disk 13.14, which receives the damping spring 40 of the second damping stage, the load friction disk 48 is likewise provided with a circumferential recess. A directional notch 49 is provided. However, since the circumferential dimension of this circumferential notch is larger than the circumferential notches provided in the driven disk and the force/S-disc, the load friction disk is It has a predetermined circumferential movement with respect to the above-mentioned disk without coming into contact with the circumferential limiting surface of the notch 49. This load friction disk 48 has two damping springs 50
The third food reduction stage is formed in cooperation with the following. The two damping springs 50 are arranged symmetrically in each case between the damping springs 40 of the second damping stage so that the force ζ-j in the disk 13, 14
It is received in longitudinal notches 51, 52 and passes through aligned circumferential notches 53, 54 in driven disk 30 and load friction disk 48, respectively. Circumferential notch 53 in driven disk 30 and load friction disk 48
．． 54 extends in the circumferential direction beyond the circumferential dimension of the damping spring 50, so that the damping spring 50 can absorb the force and force of the driven disc 30.
Only after the S-disc 13.14 has been rotated by a predetermined amount does it come into contact with the circumferential limiting surface of the circumferential notch 53 in the driven disc, and as a result, the predetermined rotation as described in A77 is made. It becomes effective only after the rotation angle has occurred.
負荷摩擦円板４８と内側の力・Ｓ−円板１４の内側の：
ｒ擦環筒の間には摩擦リング５６が配置されている。負
荷摩擦円板と内側の力・ぐ−円板との間に第２の摩擦段
に駕する押圧円板４４が配置され、この押圧円板が内側
の力・Ｓ−円板１牛に設けられた周方向切欠き内に形状
接続的に係合する軸方向に向けられた舌片４６を介して
カッζ−円阪と回動不能に結合されていることにより、
負荷摩擦円板４８は摩擦リング５６に千着され、摩擦リ
ング５６は内側の力・Ｓ−円板１４の対応する摩擦面に
対して圧着される。Load friction disk 48 and internal force・S-Inside of disk 14:
A friction ring 56 is arranged between the r friction ring cylinders. A pressure disk 44 running on the second friction stage is arranged between the load friction disk and the inner force disk 44, and this pressure disk is provided on the inner force disk 1. by being non-rotatably connected to the cutter ζ-Ensaka via an axially oriented tongue 46 which engages positively in the circumferential notch provided.
The load friction disk 48 is affixed to the friction ring 56, which is crimped against the corresponding friction surface of the inner force/S-disc 14.
これに対して被駆動円板３ｏに向がっては負荷摩擦円板
４８は所定の周方向の角度範囲に亘って自由に回転可能
である。この場合には負荷摩擦円板の軸方向に向けられ
た舌片５７は被駆動円板３０に設けられた、両側で減衰
ばね５ｏを越えて延びる周方向切欠き５３内に係合して
いる。この舌片５７は負荷摩擦円板が被駆動円板に対し
て所定量だけ回動した後でストツ・ξにあたり、次いで
その都度の回転方向で負荷摩擦円板と彼、駆動円板との
回転不ａしな結合をもたらｌ−０減衰ばね５ｏは負荷摩
擦円板４８と、これと内側の力・＄−円阪１４の摩擦面
との間に設けられた摩擦リング５６と協働して第３の１
１ｔ２哀段を形成する。On the other hand, toward the driven disk 3o, the load friction disk 48 is freely rotatable over a predetermined circumferential angular range. In this case, the axially oriented tongues 57 of the load friction disk engage in circumferential recesses 53 in the driven disk 30, which extend beyond the damping springs 5o on both sides. . This tongue piece 57 reaches the position ξ after the load friction disk has rotated by a predetermined amount with respect to the driven disk, and then rotates the load friction disk, the driver disk, and the load friction disk in the rotational direction each time. Providing a secure connection, the l-0 damping spring 5o cooperates with the load friction disk 48 and a friction ring 56 provided between this and the friction surface of the inner force 14. te third 1
Form 1t2 dan.
ねじれ振動減衰器１０の運転中に駆動部分１１から、駆
動円板１２を介してトルクが導入されると、一方では駆
動円板と力・Ｓ−円板１３，１４との間Ｇこがっ他方で
は力・ζ−円板１３ 、 ｊ４と被駆動徊１３４に回転
／Ｔ′能に結合された被駆動用１１１１ｉ３０との１間
に回動が生ぜしめられる。すると第１と第２の減衰段の
、プレーロートゝをがけられることなしに組込まれた減
衰ばね２ｏと４０は（Ｕ列に接続された状態で相応のや
わらかいばね特性で作用する。これは第３図の特性線図
の特性線Ｇｏの平らな経過で示されている。もちろんよ
り大きな回動は減衰ばねが小さな硬さを有している減衰
段で生じる。この減衰段は駆動因板］２と力・ζ−円板
１３．ｌ牛との間で作１＋１する、カ１友哀ばね２０を
有する減衰段である。If, during operation of the torsional vibration damper 10, a torque is introduced from the drive part 11 via the drive disk 12, then on the one hand there is a On the other hand, a rotational movement is produced between the force ζ-disk 13, j4 and the driven arm 1111i30, which is connected to the driven arm 134 in a rotational/T' manner. Then, the damping springs 2o and 40 of the first and second damping stages, which are assembled without being rotated by the plate rotor, act with correspondingly soft spring characteristics (when connected in the U row). This is indicated by the flat course of the characteristic line Go in the characteristic diagram of Fig. 3. Of course, greater pivoting occurs in the damping stage in which the damping spring has a small stiffness. 2 and the force/ζ-disc 13.1 is a damping stage with a force spring 20, which is created by 1+1.
この減衰段の１１．に哀ばね２０が力・ミー円板上３゜
］４にλ・ｊするｌ；動因板１２の回動によって緊縮さ
Ｊｌ、両ノＪ″の力・ζ−円板を回転不能にかつ）軸方
向にイく動にｌｒいに結合するスペーサピン１５が駆動
円板における円弧状の長孔１６の端部に接触させらねる
と、第１の減衰段の減衰ばねが遮断され、第２の減衰段
の減衰ばねだけが有効になる。第３図の特性線図では第
１の減衰段は００から２３°までの回動角度範囲に亘っ
て延びており、第１の減衰段が遮断された後の回動角度
２３°と３８°との間第２の減衰段の範囲では被駆動円
板３０とカバー円板１３．１４との間の相対運動しか行
なわれない。この場合にはｉ＋、Ｑ Ｎばね４０だけが
有効であり、この結果、第２の減衰段の範囲では特性曲
線６１は一１＝昇経過を有することになる。駆動円板１
２と被駆動円板３０との間の回動角度が３８°になると
、第３の減衰段の減衰ばね５０が被駆動円板の窓状脂膜
の減衰ばね５０が第２の減衰段の減衰ばね４０に対して
並列的に作用するようになる。このように第２の減衰段
の、’ｔ、ｆｉ衰ばね４０が第３の減衰段の減Ｑばね５
０と並列的に接続されることによって、特性線６２は強
くト昇させられる。11 of this damping stage. The spring 20 exerts a force λ j on the disk at 3°]4; it is tightened by the rotation of the dynamic plate 12, Jl, and the force ζ on both sides J'' - making the disk unrotatable and) If the spacer pin 15, which is coupled to the axially moving lr, fails to come into contact with the end of the arc-shaped elongated hole 16 in the drive disk, the damping spring of the first damping stage is cut off, and the damping spring of the second damping stage is cut off. Only the damping springs of the damping stages are activated.In the characteristic diagram in Fig. 3, the first damping stage extends over the rotational angle range from 00 to 23°; Between the rotation angles 23° and 38° after the rotation angle, in the region of the second damping stage only a relative movement between the driven disk 30 and the cover disk 13.14 takes place. Only the i+, Q N springs 40 are active, so that in the region of the second damping stage the characteristic curve 61 has a -1=rising course.Drive disk 1
When the rotation angle between 2 and the driven disc 30 reaches 38°, the damping spring 50 of the third damping stage will change, and the damping spring 50 of the window-shaped oil film of the driven disc will move away from the damping spring 50 of the second damping stage. It comes to act in parallel on the damping spring 40. In this way, the 't, fi damping spring 40 of the second damping stage is the damping spring 5 of the third damping stage.
By being connected in parallel with 0, the characteristic line 62 is strongly raised.
この特性線６２は３８°の回動角度で第２の減ヴ段の特
性線６１に接続し、４２°の回動角度で第２と第３の減
衰段の減衰ばね全体がブロックされるまで作用する。This characteristic line 62 connects to the characteristic line 61 of the second damping stage at a rotation angle of 38°, until at a rotation angle of 42° the entire damping spring of the second and third damping stage is blocked. act.
前述の如く、駆動円板１２とカバー円板との間と力・ζ
−円板と被駆動円板との間とに回動が生じた場合に減食
ばねが作用する他に、駆動円板と被駆動円板とが力・ぐ
−円板に対して相対ｊ■動した場合にも冬減衰段に配属
された摩擦段が作用する。つまり比軸的にやわらかい減
衰ばね２０を有する第１の減衰段の範囲に於ては初期回
動に際して特に駆動円板１２と力・ζ−円板１３．１４
との間の相対運動が生じ、摩擦リング２２．２３の範囲
に摩擦が生じる。駆動円板１２とツノパー円板１３ 、
］、 ４の間に所定用の回動が達成されると、カバー
円板をσいに結合するスペーサピン］５が円弧状の長孔
１６の６部に当接し、ｇ５＜動因板］−２と力・ぐ−円
板との間（、こ引続いて相対連動が生じることを阻止す
る。従って回動が進むことによって生じる摩擦はさしあ
たり第２の摩擦段を形成する摩擦リング４２，４３の範
ＩＪＮだけで行なわれる。負荷摩擦円板４８は駆動円板
１２が力・Ｓ−円板１３．１４に対して回動する間のよ
うに、周方向切欠き５３内に係合する軸）ｊ向に向けら
れた舌片５７が周方向切欠き内でストン・ξに当接し、
°これによって被駆動円板３０に対する負荷摩擦円板の
回動性が制限されるまでは、カバー円板に対して静止さ
刊られる。負荷摩擦円板の舌片５７が前述のストン・々
に当接した後で第３の摩擦段が佇効になる。この場合に
は内側の力・ζ−円板１４の対応する１情擦而と摩擦リ
ング５６を介して摩擦接続′させられた負荷摩擦円板が
前述の内側の力・七−円板に対して相対回動を行なう。As mentioned above, the force between the drive disk 12 and the cover disk ζ
- In addition to the action of the reducing spring when rotation occurs between the disc and the driven disc, the driving disc and the driven disc are subjected to force and force relative to the disc. Even when the engine moves, the friction stage assigned to the winter damping stage comes into play. This means that in the region of the first damping stage with the relatively soft damping spring 20, especially during the initial rotation, the drive disk 12 and the force ζ-disk 13.14
A relative movement between the two occurs, resulting in friction in the area of the friction ring 22,23. Drive disk 12 and horn disk 13,
], When the predetermined rotation is achieved between 4 and 4, the spacer pin 5 that connects the cover disc in a σ abuts against part 6 of the arc-shaped long hole 16, and g5<movement plate]- 2 and the force disk (this prevents a subsequent relative interlocking from occurring. Therefore, the friction caused by the progress of the rotation is initially reduced by the friction rings 42, 43 forming the second friction stage). The load friction disk 48 is driven by an axis that engages in the circumferential notch 53 during rotation of the drive disk 12 relative to the force-S disk 13.14. ) The tongue piece 57 directed in the j direction contacts the stone ξ within the circumferential notch,
° This leaves it stationary relative to the cover disc until the rotation of the load friction disc relative to the driven disc 30 is limited. After the tongues 57 of the load friction disk have abutted against the aforementioned stones, the third friction stage becomes visible. In this case, the load friction disk frictionally connected to the corresponding force of the inner force ζ disk 14 through the friction ring 56 responds to the aforementioned inner force 7 disk. to perform relative rotation.
第３の摩擦段の摩擦円板５６の範囲で行なわねる摩擦運
動は、第２の摩擦段の範囲で生じる摩擦運動に重畳させ
られる。第３図の特性線図の引張側に示されているよう
に、回動トルクが減少させられかつ互いに相対的に周方
向に運動可能な円板が戻り回転する場合にも同じ摩擦運
動がｒテなわれなければならない。特性線の引張側と同
じ関係は押し側にもあてはまる。The friction movement that takes place in the area of the friction disc 56 of the third friction stage is superimposed on the friction movement that occurs in the area of the second friction stage. As shown on the tension side of the characteristic diagram in FIG. 3, the same frictional movement r must be taught. The same relationship as for the tension side of the characteristic line also applies to the push side.
第４図と第５図に示された実施例は３段のねじれ振動減
衰器であって、第１図と第２図の実施例と同じ構成部材
には同じ符号が、しかし区別するために１００を加えて
付けられている。The embodiment shown in FIGS. 4 and 5 is a three-stage torsional vibration damper in which the same components as the embodiment of FIGS. 1 and 2 have the same reference numerals, but for distinguishing purposes. 100 is added.
トルクを一点ｍｌ ｉＦｊで示された駆動部分１１１か
ら導入するためにはこの場合にも駆動円板１１２が用い
られる。この駆動円板１１２は軸方向と回動不能に互い
に結合された力・ζ−円板１１３．１１４の間に受容さ
れている。図示されていない被駆動軸にトルクを伝達す
るためには駆動円板１１２に対しそ同軸的に配置され、
この駆動円板１１２から半径方向内側に延びる被駆動円
板１３０が用いられる。この被駆動円板１３０は同様に
カーミー円板の間に受容されている。被駆動円板がボス
側に簡１な内歯１３２をＤ：ｉｊえ、被駆動軸の対応爾
と協働するかわりに、被駆動円板のボス範囲に対応する
キー溝１３２′を有するボスフラン）１３１が一体に成
形されていてもよい。A drive disk 112 is used in this case as well to introduce the torque from the drive part 111, designated by the point ml iFj. This drive disk 112 is accommodated between axially and non-rotatably coupled force .zeta. disks 113, 114. In order to transmit torque to a driven shaft (not shown), it is arranged coaxially with the drive disk 112,
A driven disk 130 is used that extends radially inward from the drive disk 112. This driven disk 130 is likewise received between the Carmy disks. The driven disc has a simple inner tooth 132 on the boss side, and instead of cooperating with the corresponding part of the driven shaft, a boss flange having a keyway 132' corresponding to the boss range of the driven disc is used. ) 131 may be integrally molded.
第１実施例と同じように、駆動円板１１２と力・ぐ−円
板１’１３．１１４と、被駆動円板１３０と力・ζ−円
板１１３，１．１４との互いに整合する周方向切欠き１
１７，１１８．１１９には減衰ばね１２０．１４０が受
容されている。この減衰ばね１２０，１＋○は周方向で
駆動円板と被駆動円板とを力・ζ−円板に対して支持す
る。As in the first embodiment, the driving disk 112, the force/gage disk 1'13, 114, the driven disk 130 and the force/ζ disk 113, 1.14 have mutually aligned circumferences. Direction notch 1
17, 118, 119 accommodate damping springs 120, 140. This damping spring 120,1+○ supports the driving disk and the driven disk in the circumferential direction against the force/ζ disk.
しかしながら第１実施・例とは異って第１の減衰段は被
駆動円板１３０に配属されるのに対し５、第２の減衰段
は駆動円板１１２に配属されている。従ってカバー円板
１１３− 、 ｌ ｌ ４と被駆動円板１ ’３０に周
方向に分配されて配置された周方向切欠き１３６．１３
７．１３８内には第１の減衰段の全部で牛つの減衰ばね
１４０が受容されるのに対し、駆動円板１１２の範囲で
はそれぞれ両方の半部に第２の減衰段の３つの減衰ばね
１２０が配置されている。第２の減衰段のそれぞれ３つ
の減衰ばね１２０から成る減衰ばね群の間には力・ぐ−
円板１１３．１１４の周方向切欠き１５１．１５−２内
に第３の減衰段の減衰ばね１５０が配置されている。こ
れらの減衰ばね１５０は駆動用１１１ｊｌ１２の窓状の
周方向切欠き１５３を貫いて延びている。駆動円板１１
２の円弧状である周方向Ｉ、ｌＪ欠き１５３は第３減衰
段の減衰ばね１５０の長さを越えて延びているので、減
衰ばね１５０は第２の減衰段の減衰ばね１．２０と並列
的に接続されて、駆動円板１１２が第２の減衰段の減衰
ばね１２０を緊縮して回動し、第３の減衰段の減衰ばね
１５０が駆動円板に於ける円弧状の周方向切欠き１５３
の周方向の制限面にぶつかってはじめて、一方又は他方
の回転方向に有効になる。However, in contrast to the first embodiment, the first damping stage is assigned to the driven disc 130 , whereas the second damping stage is assigned to the driving disc 112 . Therefore, the circumferential recesses 136.13 arranged circumferentially distributed on the cover disks 113-, l14 and the driven disk 1'30
7.138 in which two damping springs 140 of the first damping stage are received, whereas three damping springs 140 of the second damping stage are received in each of the two halves in the region of the drive disk 112. 120 are arranged. Between the damping spring groups each consisting of three damping springs 120 of the second damping stage, a force and force are applied.
The damping spring 150 of the third damping stage is arranged in the circumferential recess 151.15-2 of the disk 113.114. These damping springs 150 extend through a window-shaped circumferential notch 153 of the drive member 111jl12. Drive disk 11
Since the circumferential arc-shaped notch 153 in the circumferential direction I, IJ extends beyond the length of the damping spring 150 of the third damping stage, the damping spring 150 is parallel to the damping spring 1.20 of the second damping stage. The drive disc 112 compresses and rotates the damping spring 120 of the second damping stage, and the damping spring 150 of the third damping stage compresses and rotates the damping spring 150 of the third damping stage. Notch 153
It becomes effective in one or the other direction of rotation only when it hits a circumferential limiting surface.
第１実施例の場合と同じように駆動円板と被駆動円板と
の間に生じる回動運動の初期では、第１と第２の減衰段
の減衰ばねは直列に接続されているので、負荷のもとて
前記駆動円板と被駆動円板との間に生じる回動に対して
はこの直列的に接続された減衰ばねの合力が作用する。As in the case of the first embodiment, at the beginning of the rotational movement occurring between the driving disk and the driven disk, the damping springs of the first and second damping stages are connected in series; The resultant force of the damping springs connected in series acts on the rotation that occurs between the driving disk and the driven disk under load.
第１と第２の減衰段の減衰ばねの共、通の作用範囲は、
この実施例では３２°の回動角度までである。これは第
６図の特性線で示されている。The common working range of the damping springs of the first and second damping stages is:
In this embodiment, the rotation angle is up to 32 degrees. This is shown by the characteristic line in FIG.
この場合には第１の減衰段の比較的にやわらかい減衰ば
ねは、力・ンー円板１１３，１１４を回転不能にかつ軸
方向に移動不能に互いに結合する、被駆動円板１３０に
於ける円弧状の長孔１１６内で周方向に運動可能なスに
一すピン１１５が前述の長孔の端部に当接し、これによ
ってその都度の回動力向で被駆動円板がカバー円板に対
してロックされる土で緊縮させられる。これによって第
１の減衰段の作用が停止させられ、後続する角度運動は
駆動円板１１２と力・ζ−円板との間°でのみ行なわれ
る。第１の減衰段の減衰ばね１４０が前述のように遮断
されることによって、約３２°の回動角度を越える角度
運動に対しては第２の減衰段の減衰ばね１２０だけが作
用する。この作用は約３８°の回動角度に達した後で第
３の減衰段の減衰はね１５０が第２の減衰段の減衰ばね
１２０に対して並列的に接続されて作用するまで行なわ
れる。従って３２°と３８°との間の回転角変範囲の第
２減衰段の特性線１６１は第２減衰段の減衰ばね１２０
のばね硬さだけによって決ポされる。これに対して第３
減衰段の特性線１６２は急勾配の上昇を呈する。この特
性線は第２と第５の減衰段の減衰ばね１２０と１５０と
の並列的な作用、ひいては個々のばね定数の和として生
じる合成ばね力によって与えられる。In this case, the relatively soft damping spring of the first damping stage is activated by a force-force force in a circle in the driven disc 130, which connects the discs 113, 114 non-rotatably and axially non-displaceably to each other. A pin 115 movable in the circumferential direction within the arc-shaped elongated hole 116 abuts against the end of the elongated hole, thereby causing the driven disk to move relative to the cover disk in the respective direction of rotation. It is tightened with soil that is locked. This stops the action of the first damping stage and subsequent angular movements only take place in degrees between the drive disk 112 and the force .zeta.-disk. Because the damping spring 140 of the first damping stage is shut off as described above, only the damping spring 120 of the second damping stage acts for angular movements exceeding a rotation angle of approximately 32°. This action takes place until, after reaching a rotation angle of approximately 38°, the damping spring 150 of the third damping stage acts in parallel connection with the damping spring 120 of the second damping stage. Therefore, the characteristic line 161 of the second damping stage in the rotational angle variation range between 32° and 38° corresponds to the damping spring 120 of the second damping stage.
It is determined only by the stiffness of the spring. On the other hand, the third
The characteristic line 162 of the damping stage exhibits a steep rise. This characteristic line is given by the parallel action of the damping springs 120 and 150 of the second and fifth damping stage and thus by the resultant spring force resulting as the sum of the individual spring constants.
第２実施例に於ても個々の減衰段に於けるばね作用には
摩擦が重畳される。しかしながら第１実施例とは異って
この場合には駆動円板１１２と被駆動円板１３０との間
のや径方向のオーバラップ範囲にしか摩擦リング１２２
が存在していない。この摩擦リング１２２は、回転不能
ではあるが、しかし軸方向に運動可能に被駆動円板１３
０と結合された押圧円板１２４を介して押圧円板と被駆
動円板１３０との間で作用する皿ばね１２５によって駆
動円板１１２に圧着される。その他の点では力・ζ−円
板と駆動円板とが相対的に回動した場合に外側の縁部で
駆動円板と力・ζ−円板との間で摩擦が有効であり、ボ
ス範囲の近くで被駆動円板と力・Ｓ−円板との間で摩擦
が有効であるような配置をとることができる。In the second embodiment as well, friction is superimposed on the spring action in the individual damping stages. However, unlike the first embodiment, in this case the friction ring 122 is placed only in the slightly radial overlap area between the driving disk 112 and the driven disk 130.
does not exist. This friction ring 122 is non-rotatable, but axially movable to the driven disk 13.
The drive disk 112 is pressed against the drive disk 112 by a disc spring 125 acting between the pressure disk and the driven disk 130 via a pressure disk 124 connected to the drive disk 130 . In other respects, when the force/ζ-disk and the drive disk rotate relative to each other, friction is effective between the drive disk and the force/ζ-disc at the outer edge, and the boss Arrangements can be made such that friction is effective between the driven disk and the force S-disc near the area.
この実施例では第１実施例とは異って、第３減衰段では
じめて有効になる付加的な負荷摩擦円板は設けられてい
ないが、この負荷摩擦円板をこの実施例でも設けること
はできる。この場合には負荷摩擦円板が被駆動円板に対
して回動することが制限されることに関連して摩擦作用
が第３減衰段の減衰はわが有効になる前又は後で働き、
いわゆる連行摩擦が生せしめられる。In contrast to the first embodiment, this exemplary embodiment does not have an additional load friction disk which becomes active only in the third damping stage, but this load friction disk could also be provided in this exemplary embodiment. can. In this case, in connection with the limited rotation of the load friction disk relative to the driven disk, the frictional effect acts before or after the damping of the third damping stage becomes effective;
This creates what is called entrainment friction.
第７〜図と第８図に示された実施例に於ても負荷の導入
は一点鎖線でしか示されていない駆動部分２１１から駆
動円板２１２を介して行なわれる。この駆動円板２１２
はこの場合にも回転不能にかつ軸方向に゛不動に互いに
結合された力・ζ−円板２１３．２１４の間に受容され
ている。In the embodiments shown in FIGS. 7-8, the introduction of the load also takes place via a drive disk 212 from a drive part 211, which is only shown in dash-dotted lines. This driving disk 212
are also in this case accommodated between the force ζ disks 213, 214, which are non-rotatably and axially fixedly connected to one another.
駆動円板２１２の半径方向内側には力・τ−内円板間に
ゼス部分２３１を備えた被駆動円板２３０が受容されて
いる。この被駆動円板は図示されていない彩式で同様に
一点鎖線でしか示されていない被駆動＠２３４と結合さ
れている。第２実施例と同様に、第１減衰段の減衰ばね
２４０は内側のばね環として被駆動円板２３０とカ・ぐ
−円板２１３，２１４の間の範囲で被駆動円板２３０と
力・Ｓ−円板２１３，２１４に設けられた互いに整合す
る周方向切欠き２３６．２３７．２３８に受容されてい
る。カッζ−円板に対する被駆動円板の回動性は、力・
ζ−円板を軸方向にかつ回動不能に豆いに結合するスペ
ーサビン２１５によって制限される。このスペーサビン
２１５は被駆動円板に於ける円弧状の長孔２１６を貫い
て延び、被駆動円板２３０と力・ζ−円板２１．３，２
１４との間に所定の回動角度が碍られると前記長孔の周
方向の制限面に当接する。これによってその都度の回転
方向で被駆動円板とカバー円板との間に回動不能な結合
が生じ、ひいては第１減衰段の減衰ばね２４０が有効で
なくなる。第２の減衰段の減衰ばね２２０は第４図と第
５図に示した実施例の場合と同じように、駆動円板２１
２と力・ぐ−円板２１３゜２１．４との間で作用するが
、第２実施例とは異ってプレロードをかけられて組込ま
れている。A driven disk 230 is received on the radially inner side of the drive disk 212 and has a force/τ-inner disk 231 with a groove 231 therebetween. This driven disc is connected in a not-illustrated manner to a driven @234, which is also shown only in dashed lines. Similar to the second embodiment, the damping spring 240 of the first damping stage acts as an inner spring ring to connect the driven disc 230 with force in the range between the driven disc 230 and the force discs 213, 214. They are received in mutually aligned circumferential notches 236, 237, 238 in the S-discs 213, 214. The rotatability of the driven disk relative to the cutter ζ disk is determined by the force and
It is limited by a spacer bin 215 which axially and non-rotatably connects the ζ-disc to the bean. This spacer bin 215 extends through an arc-shaped elongated hole 216 in the driven disc, and connects the driven disc 230 with the force/ζ-disk 21.3, 2.
14, when a predetermined rotation angle is established, the elongated hole comes into contact with the limiting surface in the circumferential direction of the elongated hole. This results in a non-rotatable connection between the driven disk and the cover disk in the respective direction of rotation, so that the damping spring 240 of the first damping stage becomes ineffective. The damping spring 220 of the second damping stage is connected to the drive disc 22 as in the embodiment shown in FIGS. 4 and 5.
2 and the force disks 213 and 21.4, but unlike the second embodiment, they are preloaded and installed.
第２の減衰段の減衰ばね２２０にプレロー１５がかけら
れていることにより、負荷がかかるとまず第１の減衰段
の減衰ばね２４０のばね力がばねの緊縮に基づいて第２
の減衰段の減衰ばね２２０のプレロードカに達するまで
は被駆動円板２３０とカバー円板２１３．２１４との間
に回動が生じる。従って明期回動では第１の減、衰段の
減衰ばね２４０しか有効でないので、第９図に示された
Ｏｏと３°との間の範囲の特性線２６０の経過は第１減
衰段の減衰ばね２４０のばね硬さだけによって決定され
る。駆動円板２１２と被駆動円板２３０との間の回動角
が大きくなると第２の減衰段の減衰ばね２２０が第１の
減衰段の減衰ばね２４０に直列的に接続されて作用し、
その結果として前記直列接続による合成ばね力が有効に
なる。直列接続による合成されたばね特性は両方の減衰
段の減衰ばね２２０．２４０の個々のばね特性よりも平
らな経過を有しているので、約３°の回動角度を越える
角度運動は第９図に示された特性線２６１の平らな経過
を決定する。この特性線２６１は図示の実施例の場合に
はほぼ１４°まで延びている。Since the pre-low 15 is applied to the damping spring 220 of the second damping stage, when a load is applied, the spring force of the damping spring 240 of the first damping stage is first changed to the second damping spring 240 based on the tension of the spring.
A rotational movement occurs between the driven disk 230 and the cover disk 213, 214 until the preload force of the damping spring 220 of the damping stage is reached. Therefore, in the light phase rotation, only the damping spring 240 of the first damping stage is effective, so that the course of the characteristic line 260 in the range between Oo and 3° shown in FIG. It is determined solely by the spring stiffness of damping spring 240. When the rotation angle between the driving disk 212 and the driven disk 230 increases, the damping spring 220 of the second damping stage is connected in series with the damping spring 240 of the first damping stage and acts,
As a result, the resultant spring force due to the series connection becomes effective. The combined spring characteristic due to the series connection has a flatter profile than the individual spring characteristics of the damping springs 220, 240 of both damping stages, so that angular movements exceeding a rotation angle of approximately 3° are not possible in FIG. Determine the flat course of the characteristic line 261 shown in FIG. This characteristic line 261 extends approximately 14° in the exemplary embodiment shown.
従って減衰段の一方にプレロードのかけられた減衰ばね
を使用することによって次第に減少する特性線経過が実
現可能である。By using a prestressed damping spring on one of the damping stages, a tapered characteristic curve can therefore be realized.
第１と第２の減衰ばねの直列的な接続は駆動円板２１２
と力・ζ−円板２１３，２１４の間の角度運動が進むと
駆動円板２１２とカバー円板２１３．２１４との間で有
効になるストツ・ξによλて約１４°の回動角度で解消
される。この場合にはその都度の回転Ｊｊ向で駆動円板
と力・↑−円阪との間に回転不能な結合が生ぜしめられ
る６、このようにして第２の減衰段の減衰ばね２２０が
遮断された後では、それ以Ｆの角度運動１１ 明ｔｕ＋
の回ωＪ範ｊＪ［（Ｇこ衿て１４独で作用する第１のｔ
Ｌｋ ！ｒ−！：段の滅ヴばね２４ ’Ｏの作用に抗し
てのみ、Ｉ、かもカバー円板と被駆動円板との間で作用
するストツ・？が当接し、これによってその都変の回転
−Ｊｊ向で被駆動円板も力・ぐ−円板と回転不能に結合
されるまで行なわれる。このストツ・ξは力・Ｓ−円板
２１３ 、２ ］−４をｉｌ＃［＋方向にかつ回動不能
に１７．いに結合するスペーサぎン２１５ カラ成って
いる。このス・く−サビン２１５は被駆動円板２３０に
於ける円弧状の長孔２〕−６を貫いて延びている。第９
図に於ては平らに延びる中央の１、テ性線２６１に続く
急勾配の特性線２６２で駆動円板の力・Ｓ−円板に対す
る回動性が口゛ンクされた後での運転状態が示されてい
る。The series connection of the first and second damping springs is provided by a drive disk 212.
and the force ζ - As the angular movement between the discs 213, 214 progresses, the force ξ that becomes effective between the drive disc 212 and the cover discs 213, 214 creates a rotation angle of approximately 14° due to the force ξ. will be resolved. In this case, a non-rotatable connection is created between the drive disk and the force ↑-Ensaka in the respective direction of rotation Jj, 6 and in this way the damping spring 220 of the second damping stage is disconnected. After that, the angular motion of F11 明tu+
times ωJ range jJ[(G
Lk! r-! : Only against the action of the stage deactivation spring 24'O is the force acting between the cover disc and the driven disc I? abut, thereby causing the rotation of the driven disk in the -Jj direction until the driven disk is also non-rotatably connected to the force disk. This force ξ is the force S-disc 213 , 2 ]-4 in the + direction and unrotatably 17. It consists of a spacer pin 215 that connects to the base. This spacer bin 215 extends through the arc-shaped elongated hole 2]-6 in the driven disc 230. 9th
In the figure, the operating state after the force of the drive disk and the rotational ability with respect to the S-disk are determined by the characteristic line 262 with a steep slope following the flat center line 1 and the characteristic line 261. It is shown.
この実施め］に於ても駆動円板２１２と被駆動円板２３
０との間の矛−・Ｓラツゾ範囲に摩擦リング２２２が配
置されており、同様に摩擦リング２２３が駆動円板と内
側のカバー円板２１４−の間に配置されている。別の摩
擦リング２４２は第１の減衰段の減衰ばね２４０の半径
方向内側で被駆動円板２３０に接触させられている。In this implementation, the driving disc 212 and the driven disc 23 are also
A friction ring 222 is arranged in the range between the drive disc and the inner cover disc 214, and a friction ring 223 is likewise arranged between the drive disc and the inner cover disc 214. A further friction ring 242 is brought into contact with the driven disk 230 radially inside the damping spring 240 of the first damping stage.
この摩擦リング２４２は外側の力・ζ−円板と回転不能
に結合された抑圧円板２４４を介して皿ばね２４５によ
って圧着されている。従って被駆動円板２３０が力・ぐ
−円板２１３．２１４に対して回動した場合に被駆動円
板のボス側の摩擦リング２４２の範囲と被駆動円板２３
０と駆動円板２１２との間の摩擦リング２２２の範囲と
に於て摩擦が生じる。第２の摩擦段としては、駆動円板
２１２が力・ぐ−円板２１３，２１４に対して回動した
場合に駆動円板と後方のカバー円板２１４との間の摩擦
リング２２３の範回に摩擦が生じる。同様に駆動円板と
被駆動円板との間に角度運動が生じた場合にはこの両方
の円板の間で作用する摩擦リング２２２の範囲に摩擦が
生じる。急勾配で上昇する約１４°と］５５゜の間の・
１う囲に於ける特性線２６２によってあられされる運転
範囲に於ては、駆動円板と被駆動円υノとの間に受容さ
れた摩擦リング２２２の範囲と破１１λ２動側のボス側
の摩擦リング２４２の範囲とに［早〕擦が生じる。これ
によってねじね振動ｉ１．ｌｓ ＋；、ｔ’ ？ｊ：の
ずべての運転１扼囲に於て減衰ばねの有効性に１９１Ｎ
擦がＩＲ畳されることが明らかである。This friction ring 242 is pressed by a disk spring 245 via a suppression disk 244 which is non-rotatably connected to the outer force/ζ disk. Therefore, when the driven disc 230 rotates relative to the force/gravity discs 213 and 214, the area of the friction ring 242 on the boss side of the driven disc and the driven disc 23
0 and the area of the friction ring 222 between the drive disk 212 and the drive disk 212. As a second friction stage, when the drive disc 212 rotates with respect to the force and force discs 213 and 214, the range of the friction ring 223 between the drive disc and the rear cover disc 214 is friction occurs. Similarly, if an angular movement occurs between the driving and driven discs, friction will occur in the area of the friction ring 222 acting between the two discs. Between approximately 14° and ]55°, which rises at a steep slope.
In the operating range defined by the characteristic line 262 in the 1st circle, the range of the friction ring 222 received between the driving disk and the driven circle υ and the 11λ2 boss side on the moving side are Premature rubbing occurs in the area of the friction ring 242. This causes screw vibration i1. ls +;, t'? j: 191 N for the effectiveness of the damping spring during one full operating cycle.
It is clear that the rub is IR folded.
図１１＋ｉは本発明の複数の実施例を示すものであって
、第１図は３つの減衰段を有するねじれ振動減食器の第
１実施例を示す部分平面図、第２図は第１図のＩｔ −
Ｉｔ線に沿った断面図、第３図は引張ｆｌｌｌｌと押し
側とのための回動角度に閃連した回動トルクの経過を示
す特性線図、第４−図は３段式のねじれ振動減食器の第
２実施例の部分゛１へ面図、第５図は第４図のＶ−Ｖ線
に沿った断面図、第６図は第４［４と第５図のねじね振
動域’ｒ−！： ＋＞の第３図に相当する特性線図、第
７図は２段式ねじれ振動減食器の部分的平面図、第８図
は第７図のｔ’１ｌｌ−■線に沿った断面図、第９図は
第７図と第８図のねじれ振動減食器の第３図に相当する
特性線図である。
１０・・・ねじれ振動減衰器、１１・・・駆動部分、１
２・・・駆動円板、１３．１４・・・力・ζ−円板、１
５・・スペーサピン、１６・・・長孔、１７ 、１８
。11+i show a plurality of embodiments of the present invention, in which FIG. 1 is a partial plan view of a first embodiment of a torsional vibration damping device having three damping stages, and FIG. It-
A cross-sectional view along the It line, Figure 3 is a characteristic diagram showing the course of rotational torque in relation to the rotation angle for tension and push sides, and Figure 4 is a three-stage torsional vibration diagram. FIG. 5 is a sectional view taken along the line V-V in FIG. 4, and FIG. 6 is a cross-sectional view of the second embodiment of the reduced tableware. 'r-! : Characteristic diagram corresponding to Fig. 3 of +>, Fig. 7 is a partial plan view of the two-stage torsional vibration reducing tableware, Fig. 8 is a sectional view taken along the t'1ll-■ line in Fig. 7. , FIG. 9 is a characteristic diagram corresponding to FIG. 3 of the torsional vibration reducing tableware of FIGS. 7 and 8. 10... Torsional vibration damper, 11... Drive part, 1
2... Drive disk, 13.14... Force/ζ-disc, 1
5... Spacer pin, 16... Long hole, 17, 18
.
Claims (1)
ー円板の間に受容された駆動円板と被、駆動円板とを有
し、この駆動円板と被駆動円板とが周方向に互いに相対
的にかつそれぞれカバー円板に対して運動可能でかつ力
・ζ−円板に対して周方向に互いに無関係に、力・Ｚ−
円板と駆動円板若しくは被駆動円板とに周方向に分配さ
れて設けられた周方向切欠き内に受容された周方向に作
用する減衰ばねから成るそれぞれ１つの減衰ばね群を介
して支えられているねじれ振動減衰器に於て、駆動円板
（１２，１１２，２１２）とカッζ−円板（１３，１４
；１１３，１１４；２１３，２１４）との間とカッζ−
円板（１３，１４；１１３゜１１４；２１３．２１４）
と被駆動円板（３０，１３０，２３０）との間にこれら
の円板の間に相対運動が生じた場合に有効である摩擦段
がそれぞれ１つ設けられていることを特徴とする、ねじ
れ振動減衰器。 ２ 各減衰ばね群の減衰ばね（２０，４０，５０；１２
０，１４０，１５０； ２２０．２４０）が互いに並列
的に接続されており、両方の減衰ばね群が互いに直列的
に接続されている、特許請求の範囲第１項記載のねじれ
振動減衰器。 ３、各減衰ばね群の減衰ばね（２０，４０、５０；１２
０，１４０，１５０；２２０，２４０）が互いに同じば
ね硬さを有している、特許請求の範囲第１項又は第２項
記載のねじれ振動減衰器。 ４、 異なる減衰ばね群の減衰ばね（２０，４０，５０
；１２０，１４０，１５０； ２２０ 。 ２４０）が異なるばね硬さを有している、特許請求の範
囲第１項から第３項までのいずれか１つの項に記載のね
じれ振動減衰器。 ５、駆動円板（１２，１１２，２１２）及び（又は）被
駆動円板（３０，１３０，２３０）のカバー円板（１３
，１４；］ １３，１１４； ２］ ３．２１４）に対
する相対運動性が少なくとも１つの周方向に作用するス
トン・ξ（１５，１６；１１５，１１６；２１５．２１
６）によって所定の回動角度に制限されている、特許請
求の範囲第１項から第４項までのいずれか１つの項に記
載のねじれ振動減衰器。 ６ ストン・”（１５，１１５，２１５）がカッぐ一円
板と固定的に結合されておりかつ駆動円板（１２，１１
２，２１２）および（又は）被駆動円板（３０，１３０
，２３０）において所定の角度に亘って延びる円弧状の
切欠き（１６，１１６，２１６）に係合している、特許
請求の範囲第５項記載のねじれ振動減衰器。 ７ ストン・ξが駆動円板（１２，１１２，２１２）若
しくは被駆動円板（３０，１３０，２３０）に於ける円
弧状の切欠き（１６，１１６，２１６）を軸方向に貫く
、力・ぐ−円板を互いに結合するピン（１５、ｌ ］、
５ 、２１５）、である、特許請求の範囲第６項記載
のねじれ振動減衰器。 ８、 少なくとも１つの減衰ばね群の減衰ばね（２０，
１２０，２２０）若しくは（４０，１４、，０，２４０
）にゾレロートゞがかけられている、特許請求の範囲第
１項から第７項までのいずれか１つの項に記載のねじれ
振動減衰器。 ９、駆動円板（１２，１１２）と力・々−一円板１３．
１４；１１３，１１４）との間若しくはカッぐ一円板（
１３，１４；１１３，１１りと被駆動円板（３０，１３
０）との間の回動が所定の回動角度に達した後ではじめ
て作用する減衰ばね群が設けられている、特許請求の範
囲第１項から第８項までのいずれか１つの項に記載のね
じれ振動減衰器。 １０ 所定の回動角度に達した後ではじめて作用する
減衰ばね群の減衰ばね（５０；１５０）が回転不能に力
・ぐ−円板（１３，１４；１１３．１１４）と結合され
ておりかつ円弧状の切欠き（５３，１５３）に受容され
ており、この切欠き（５３，１５３）が駆動円板（１２
，１１２）若しくは被、駆動円板（３０，１３０）にオ
６いて両側で所定の程度だけ前記減衰ばね群の減衰ばね
の長さを越えて周方向に延びている、特許請求の範囲第
９項記載のねじれ振動減衰器。 １１ 駆動円板（１２）と力・ぐ−円板との間及び（
又は）カバー円板と被駆動円板（３０）との間に所定の
回動角度に達した後ではじめて有効になる負荷摩擦段が
設けられている、特許請求の範囲第１項から第１Ｏ項ま
でのいずれか１つの項に記載のねじれ振動減衰器。 １２、駆動円板（１１２，２１２）と被駆動円板（１３
０，２３０’）との間に直接的に作用する摩擦段が設け
られている、特許請求の範囲第１項から第１１項までの
いずれか１つの項に記載のねじれ振動減衰器。 １３、各摩擦段に、周方向に互いに相対的に運動可能な
円板の摩擦面に圧着された少なくとも１つの摩擦リング
（２２，２３，４２，４３，５６；１２２；２２２，２
２３，２４２）が配置されている、特許請求の範囲第１
項から第１２項までのいずれか１つの項に記載のねじれ
振動減衰器。 ■４．少なくとも１つの摩擦段において摩擦リングが、
制限されて軸方向に運動可能に支承された抑圧円板（２
４，４！、４８；１２４；２４４）を介して、周方向に
互いに相対的に運動可能な円板の１つの摩擦面に圧着さ
れているのに対し、抑圧円板がばね力で負荷され、摩擦
段に於て協働する円板の他方の円板に回転不能に支承さ
れている、特許請求の範囲第１３項記載のねじれ振動減
衰器。 １５、負荷摩擦段がばね力で負荷された摩擦円板（４８
）を有し、この摩擦円板（４８）が周方向で互いに相対
的に運動可能な円板の間に軸方向に運動可能にかつこれ
らの円板の一方に対して所定の回動角度だけ摩擦なしで
回動可能に支承されているが所定の回動角度だけ進んだ
あとてＸその都度の回転方向で回動不能に１１Ｓ記円板
と結合されている、特許請求の範囲第］−３項記載のね
じれ振動減衰器。 １６ 抑圧円板若しくは摩擦円板を圧着するためにそ
れぞれ１つの皿ばね（２５，４５；１２５；２４５）が
用いられている、特許請求の範囲第４４項又は第１５項
記載のねじれ振動減衰器。[Scope of Claims] - a drive disk and a cover received between cover disks which are triaxially and non-rotatably connected to each other; The drive discs are movable in the circumferential direction relative to each other and in each case relative to the cover disc, and exert a force Z- on the discs in the circumferential direction independently of each other.
supported via a respective damping spring group of circumferentially acting damping springs received in circumferential recesses distributed circumferentially in the disc and in the drive or driven disc; In the torsional vibration damper shown in FIG.
;113,114;213,214) and Ka ζ-
Disc (13, 14; 113° 114; 213.214)
and the driven disk (30, 130, 230), characterized in that a friction stage is provided in each case, which is effective in the case of a relative movement between these disks. vessel. 2 Damping springs of each damping spring group (20, 40, 50; 12
220.240) are connected in parallel with each other and both damping spring groups are connected in series with each other. 3. Damping springs of each damping spring group (20, 40, 50; 12
The torsional vibration damper according to claim 1 or 2, wherein the springs (0, 140, 150; 220, 240) have the same spring hardness. 4. Damping springs of different damping spring groups (20, 40, 50
;120,140,150;220. Torsional vibration damper according to any one of claims 1 to 3, wherein the springs 240) have different spring stiffnesses. 5. Cover disk (13) of drive disk (12, 112, 212) and/or driven disk (30, 130, 230)
, 14;] 13, 114;
6) The torsional vibration damper according to any one of claims 1 to 4, wherein the torsional vibration damper is limited to a predetermined rotation angle by 6). 6 "stone" (15, 115, 215) is fixedly connected to the cutting disc and the drive disc (12, 11
2,212) and/or driven disc (30,130
, 230), the torsional vibration damper is engaged with an arcuate notch (16, 116, 216) extending over a predetermined angle. 7. The force that causes the stone ξ to axially penetrate the arc-shaped notch (16, 116, 216) in the driving disc (12, 112, 212) or the driven disc (30, 130, 230). - pins (15, l) connecting the discs to each other;
5, 215), the torsional vibration damper according to claim 6. 8. damping springs of at least one damping spring group (20,
120,220) or (40,14,,0,240
8. A torsional vibration damper according to any one of claims 1 to 7, wherein the torsional vibration damper is provided with a Sollerot. 9. Drive disc (12, 112) and force-1 disc 13.
14; 113, 114) or a circular plate (
13, 14; 113, 11 and the driven disc (30, 13
0) is provided with a damping spring group that acts only after the rotation between the two ends reaches a predetermined rotation angle. Torsional vibration damper as described. 10 The damping springs (50; 150) of the damping spring group, which act only after a predetermined rotation angle is reached, are non-rotatably connected to the force disks (13, 14; 113, 114) and It is received in an arc-shaped notch (53, 153), and this notch (53, 153)
, 112) or the drive disc (30, 130) and extending in the circumferential direction beyond the length of the damping springs of the damping spring group by a predetermined extent on both sides. Torsional vibration damper as described in Section 1. 11 Between the drive disk (12) and the force disk and (
or) a load friction stage is provided between the cover disc and the driven disc (30) which becomes active only after a predetermined rotational angle has been reached. A torsional vibration damper according to any one of the preceding clauses. 12, driving disc (112, 212) and driven disc (13
12. A torsional vibration damper according to claim 1, wherein a friction stage is provided which acts directly between the torsional vibration damper (0,230'). 13. In each friction stage, at least one friction ring (22, 23, 42, 43, 56; 122; 222, 2
23,242) is arranged.
12. The torsional vibration damper according to any one of paragraphs 1 to 12. ■4. In at least one friction stage a friction ring comprises:
a restraining disk (2) mounted for limited axial movement;
4,4! , 48; 124; 244) to the friction surface of one of the discs movable relative to each other in the circumferential direction, while the suppression disc is loaded with a spring force and presses against the friction stage. 14. A torsional vibration damper according to claim 13, wherein the torsional vibration damper is non-rotatably supported on the other of the cooperating discs. 15. The load friction stage is a friction disk loaded with a spring force (48
), the friction disk (48) is movable in the axial direction between disks that are movable relative to each other in the circumferential direction, and is friction-free with respect to one of these disks by a predetermined rotation angle. X is rotatably supported at X, but after advancing by a predetermined rotation angle, X is unrotatably coupled to the disc 11S in the respective rotational direction, Claim No.]-3 Torsional vibration damper as described. 16. Torsional vibration damper according to claim 44 or claim 15, in which a disc spring (25, 45; 125; 245) is used for crimping the suppression disc or the friction disc, respectively. .
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE32278098 | 1982-07-24 | ||
| DE19823227809 DE3227809A1 (en) | 1982-07-24 | 1982-07-24 | TORQUE Vibration DAMPER, ESPECIALLY FOR MOTOR VEHICLE DRIVERS EQUIPPED WITH TORQUE CONVERTERS |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5934024A true JPS5934024A (en) | 1984-02-24 |
| JPH0444138B2 JPH0444138B2 (en) | 1992-07-20 |
Family
ID=6169319
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13452783A Granted JPS5934024A (en) | 1982-07-24 | 1983-07-25 | Torsional vibration damper |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS5934024A (en) |
| BR (1) | BR8303924A (en) |
| DE (1) | DE3227809A1 (en) |
| FR (1) | FR2530752A1 (en) |
| GB (1) | GB2124334B (en) |
Cited By (2)
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|---|---|---|---|---|
| JPS60260760A (en) * | 1984-05-29 | 1985-12-23 | イートン コーポレーシヨン | Torsional variable absorption mechanism |
| JPS61252962A (en) * | 1985-04-30 | 1986-11-10 | Aisin Warner Ltd | Directly-coupled clutch for hydraulic transmission |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3448510C2 (en) * | 1983-11-15 | 1996-12-05 | Luk Lamellen & Kupplungsbau | IC engine torque variation compensator |
| FR2573150B1 (en) * | 1984-11-09 | 1987-02-13 | Valeo | TRANSMISSION ASSEMBLY, PARTICULARLY FOR A MOTOR VEHICLE, HYDRAULIC COUPLING MEMBER COMPRISING SUCH A TRANSMISSION ASSEMBLY, DEVICE FOR TAKING MOTION SPECIFICALLY THEREOF, AND METHOD FOR THE PRODUCTION OF THIS DEVICE FOR MOVEMENT |
| DE8509108U1 (en) * | 1985-03-27 | 1992-12-10 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Device for compensating torsional shocks |
| DE3610735A1 (en) * | 1985-04-04 | 1986-10-09 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | DEVICE WITH AT LEAST TWO RELATIVELY TURNING FLYING EQUIPMENT PROVIDED DAMPING DEVICE AND SLIP CLUTCH |
| US4716998A (en) * | 1985-04-30 | 1988-01-05 | Aisin Warner Kabushiki Kaisha | Direct coupling clutch with a damper device for a fluid coupling |
| DE8525579U1 (en) * | 1985-09-07 | 1993-06-03 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Device for compensating torsional shocks |
| JP2718413B2 (en) * | 1986-07-05 | 1998-02-25 | ルーク・ラメレン・ウント・クツプルングスバウ・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング | Vibration damper |
| DE3745090C2 (en) * | 1986-07-05 | 2002-03-07 | Luk Lamellen & Kupplungsbau | Flywheel with torsional vibration damping |
| DE3721711C2 (en) * | 1986-07-05 | 1997-09-04 | Luk Lamellen & Kupplungsbau | Device for damping vibrations |
| DE4333562C5 (en) * | 1992-10-12 | 2008-01-17 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Power transmission device |
| DE19544832C2 (en) * | 1995-12-01 | 1998-01-22 | Patentverwertung Ag | clutch |
| JPH10153238A (en) * | 1996-11-14 | 1998-06-09 | Patentverwert G Rohs Voigt Mbh | Fluid type twisting vibration damping device |
| WO2007128267A1 (en) | 2006-05-04 | 2007-11-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transmission device |
| FR3053424B1 (en) * | 2016-07-01 | 2018-07-27 | Valeo Embrayages | TORSION DAMPER |
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| JPS5259860U (en) * | 1975-10-29 | 1977-04-30 | ||
| JPS5417110A (en) * | 1977-06-02 | 1979-02-08 | Mosbach Klaus H | Production of magnetic polymer particle supporting drug |
| JPS5694049A (en) * | 1979-12-26 | 1981-07-30 | Borg Warner | Two stage torsion and vibration damper |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1520684A (en) * | 1967-03-02 | 1968-04-12 | Ferodo Sa | Improvements to the clutch friction discs with damper hubs |
| FR2162702A5 (en) * | 1971-11-29 | 1973-07-20 | Ferodo Sa | |
| FR2386729A1 (en) * | 1977-04-04 | 1978-11-03 | Ferodo Sa | TORSION DAMPER, IN PARTICULAR CLUTCH FRICTION, ESPECIALLY FOR MOTOR VEHICLES |
| FR2456264A1 (en) * | 1979-05-11 | 1980-12-05 | Ferodo Sa | TORSION DAMPING DEVICE, IN PARTICULAR A CLUTCH FRICTION, IN PARTICULAR FOR A MOTOR VEHICLE |
| JPS6014212B2 (en) * | 1980-09-25 | 1985-04-12 | 株式会社大金製作所 | damper disc |
| FR2500557B1 (en) * | 1981-02-25 | 1985-06-14 | Valeo | TORSION DAMPING DEVICE, IN PARTICULAR A CLUTCH FRICTION, IN PARTICULAR FOR A MOTOR VEHICLE |
| US4422535A (en) * | 1981-05-20 | 1983-12-27 | Ford Motor Company | Compound damper assembly for an automatic transmission |
| DE3145312A1 (en) * | 1981-11-14 | 1983-05-26 | Fichtel & Sachs Ag, 8720 Schweinfurt | CLUTCH DISC WITH TORSION VIBRATION DAMPER WITH LEVELING DAMPING SYSTEMS |
-
1982
- 1982-07-24 DE DE19823227809 patent/DE3227809A1/en not_active Ceased
-
1983
- 1983-07-22 FR FR8312156A patent/FR2530752A1/en not_active Withdrawn
- 1983-07-22 BR BR8303924A patent/BR8303924A/en unknown
- 1983-07-25 GB GB08320027A patent/GB2124334B/en not_active Expired
- 1983-07-25 JP JP13452783A patent/JPS5934024A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5259860U (en) * | 1975-10-29 | 1977-04-30 | ||
| JPS5417110A (en) * | 1977-06-02 | 1979-02-08 | Mosbach Klaus H | Production of magnetic polymer particle supporting drug |
| JPS5694049A (en) * | 1979-12-26 | 1981-07-30 | Borg Warner | Two stage torsion and vibration damper |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60260760A (en) * | 1984-05-29 | 1985-12-23 | イートン コーポレーシヨン | Torsional variable absorption mechanism |
| JPS61252962A (en) * | 1985-04-30 | 1986-11-10 | Aisin Warner Ltd | Directly-coupled clutch for hydraulic transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2124334B (en) | 1986-01-08 |
| FR2530752A1 (en) | 1984-01-27 |
| JPH0444138B2 (en) | 1992-07-20 |
| GB8320027D0 (en) | 1983-08-24 |
| BR8303924A (en) | 1984-04-10 |
| GB2124334A (en) | 1984-02-15 |
| DE3227809A1 (en) | 1984-01-26 |
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