JPS6136533A

JPS6136533A - Device for absorbing rotary shock of internal combustion engine

Info

Publication number: JPS6136533A
Application number: JP14847085A
Authority: JP
Inventors: パウル・マウヒヤー; オズヴアルト・フリードマン
Original assignee: LuK Lamellen und Kupplungsbau GmbH
Current assignee: LuK Lamellen und Kupplungsbau GmbH
Priority date: 1984-07-07
Filing date: 1985-07-08
Publication date: 1986-02-21
Anticipated expiration: 2011-10-30
Also published as: JPH0754924A; JP2795337B2; JP3217672B2; JPH0771523A; JP2550020B2; JP3062006B2; JPH09189343A; JP2965853B2; JPH0754923A; JPH0771524A; JP3342952B2

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】産業上の利用分野本発明は、内燃機関の回転衝撃、市にモーメント変動を
吸収するための装置であって、少なくとも２つの、互い
に同軸的に配置された、減衰装置の作用に抗して制限さ
れて互いに回動可能なはずみ質量体を有し、これらのは
ずみ質量体の一方が内燃機関と結合されかつ他方のはず
み質量体が伝動装置の入力部と結合可能であって、減衰
装置が周方向に有効な蓄力器及び（又は）摩擦又は滑り
部材から成っており、この減衰装置に対して付加的に少
なくとも１つの第２の減衰装置がはずみ質量体の間のト
ルク伝達路に設けられている形式のものに関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The invention relates to a device for absorbing rotational shocks and moment fluctuations of an internal combustion engine, comprising at least two damping devices arranged coaxially with respect to each other. the propelling masses are rotatable with respect to each other in a limited manner against the action of the damping device consists of a circumferentially effective force accumulator and/or a friction or sliding element, and in addition to this damping device at least one second damping device is provided between the spring masses. It relates to a type of torque transmission path provided in

発明の課題本発明の課題は上記形式の装置を、特にその構成又は構
造及び耐摩耗性及び機能に関°して改良し、更に当該装
置の使用可能領域を拡大することである。また当該装置
の安価な製造も保証されなければならない。OBJECTS OF THE INVENTION It is an object of the invention to improve a device of the type described above, in particular with regard to its composition or structure, wear resistance and function, and to further widen the range of possible use of the device. It must also be ensured that the device is inexpensive to manufacture.

課題を解決するための手段上記の課題は本発明によれば、第１の減衰装置と第２の
減衰装置がそれぞれ少なくとも２つの軸方向に間隔をお
いて配置された円板を有し、各円板グループが他方のは
ずみ質量体に回動不能であって、両方の円板グループの
間で有効な共通の中間フランジが第１と第２の減衰装置
との間で回転モーメントを伝達するために設けられてい
ることによって解決された。SUMMARY OF THE INVENTION According to the invention, the first damping device and the second damping device each include at least two axially spaced discs, each of which a group of discs is non-rotatable to the other bouncing mass, and a common intermediate flange active between both groups of discs transmits rotational moments between the first and second damping device; This problem was solved by the following.

実施態様本発明の有利なｌ実施態様によれば、中間フランジが半
径方向で両方の円板グループを便っているとよく、この
際に軸線方向で特に短い構造体長さを保証するために更
に、一方の円板グループがほぼ半径方向で他の円板グル
ープの内側に設けられており、フランジが両方の円板グ
ループを半径方向で覆っていると有利である。Embodiment According to an advantageous embodiment of the invention, it is possible for the intermediate flange to cover both disc groups in the radial direction, with additional features being provided in order to ensure a particularly short structural length in the axial direction. Advantageously, one disk group is arranged approximately radially inside the other disk group, and the flange radially covers both disk groups.

更に本発明の有利な実施態様によれば、第２の減衰装置
の入力部が第１のはずみ質量体と結合された円板グルー
プから構成され、出力部が第１の減衰装置の入力部をも
構成する中間フランジによって構成されておυ、第１の
減衰装置の出力部が第２のはずみ質量体と結合された両
方の円板によって構成されている。この際に特に有利に
は、両方のはずみ車の相互回動を可能とするために、中
間フランジと半径方向内側の円板グループの間及び（′
又は５中間フラ／）と半径方向外側の円板グループとの
間に形状接続による結合が形成されているとよい。この
ような形状接続による結合は、フランジ及び一方又は両
方の円板グループに当付は輪郭部を形成し、その両輪郭
部を確実に相互協働させることによって可能である。Furthermore, according to an advantageous embodiment of the invention, the input part of the second damping device is constituted by a group of discs connected to the first floating mass, and the output part is connected to the input part of the first damping device. The output part of the first damping device is also constituted by the intermediate flange which also constitutes the second spring mass, and the output part of the first damping device is constituted by the two discs which are connected to the second spring mass. In this case, it is particularly advantageous to provide a space between the intermediate flange and the radially inner disk group and ('
Alternatively, a form-fitting connection may be formed between the intermediate plate/) and the radially outer disk group. Such a form-fitting connection is possible in that the flange and one or both disk groups are provided with contours which ensure mutual cooperation.

更に本発明によれば、第１の減衰装置の円板グループが
、伝動装置の入力部と結合可能な第２のはずみ質量体と
回動不能であって、第２の減衰装置が、内燃機関と結合
された第１のはずみ質量体と回動不能であると有利であ
る。しかしまた、第１の減衰装置の円板グループが第１
のはずみ質量体と回動不能であって、第２の減衰装置の
円板グループが第２のはずみ質量体と回動不能であって
もよい。Furthermore, according to the invention, the disc group of the first damping device is non-rotatable with a second floating mass connectable to the input of the transmission, and the second damping device Advantageously, it is non-rotatable with respect to the first bouncy mass which is connected to the first spring mass. However, it is also possible that the disk group of the first damping device
may be non-rotatable with respect to the bouncing mass, and the disc group of the second damping device may be non-pivotable with the second bouncy mass.

更に第２の減衰装置の特に単純な構造を保証するために
、中間フランジが、滑りモーメーントを形成する第２の
減衰装置の円板グループの間で軸方向に緊締されている
とよい。この場合、必要な滑りモーメントの大きさによ
っては、フランジと第２の減衰装置の両回板とが直接に
摩擦接触せしめられると有利である。しかし大抵の使用
例においては有利には、少なくとも第２の減衰装置の円
板の１つとフランジとの間に摩擦ライニング又は滑りラ
イニングが設けられ、それによってその都度の使用例に
合、わせて適当な摩擦又は滑りライニングを用いること
が可能であるとよい。Furthermore, in order to ensure a particularly simple construction of the second damping device, it is advantageous if the intermediate flange is clamped axially between the disk groups of the second damping device that form the sliding moment. In this case, depending on the magnitude of the required sliding moment, it may be advantageous if the flange and the two discs of the second damping device are in direct frictional contact. However, in most applications it is advantageous to provide a friction lining or a sliding lining between at least one of the discs of the second damping device and the flange, so that it can be adapted to suit the particular application. It may be possible to use a friction or slip lining.

第２の減衰装置の円板グループの間へのフランジの軸方
向緊締を確実にするために有利には、第２の減衰装置の
一方の円板が軸方向ではずみ質量体の１つに固定されて
おり、他方の円板が前記円板に対して軸方向に移動可能
であるとよい。まだこの際Ｋ、軸方向に固定された円板
が他方の円板の回動を防止するようになっていると有利
である。この第２の減衰装置）両方の円板の間での回動
防止は有利には、回動を防止するために第２の減衰装置
の円板の一方が軸方向の突起を有し、この突起が他方の
円板の切欠きに係合していることによって可能である。In order to ensure axial tightening of the flange between the groups of discs of the second damping device, one disc of the second damping device is advantageously fixed axially to one of the spring masses. It is preferable that the other disk is movable in the axial direction with respect to the disk. In this case, it is still advantageous if the axially fixed disk prevents the other disk from pivoting. This prevention of rotation between the two discs (of this second damping device) is advantageous in that one of the discs of the second damping device has an axial projection in order to prevent rotation. This is possible by engaging the notch in the other disc.

更にこの際に特に単純な構成としては、突起が少なくと
も一方の円板に一体成形された、軸方向に延びる舌状部
により形成されており、この舌状部が他方の円板の外周
に設けられた切欠きに軸方向で突入していると有利であ
る。また使用例に応じて、この突起を、第２の減衰装置
の軸方向固定された円板及び（又は）軸方向移動可能な
円板が有していてもよい。更に軸方向の突起が第２の減
衰装置の円板の少なくとも１つの、半径方向で見て外周
に設けられており、それによってこの突起が中間フラン
ジの外側を軸方向で覆っていると有利である。また第２
の減衰装置の円板の少なくとも１つをはずみ質量体の１
つに軸方向で固定することが、本発明によれはリベノ）
［よって行なわれると有利である。Furthermore, a particularly simple construction in this case is such that the projection is formed by an axially extending tongue formed integrally on at least one of the disks, which tongue is provided on the outer periphery of the other disk. Advantageously, it projects axially into the cutout. Depending on the application, the axially fixed and/or axially movable disc of the second damping device may also have this projection. Furthermore, it is advantageous if an axial projection is provided on the radially outer circumference of at least one of the disks of the second damping device, so that this projection covers the outside of the intermediate flange in the axial direction. be. Also the second
one of the mass bodies that impels at least one of the discs of the damping device of
According to the invention, it can be fixed axially to
[Therefore, it is advantageous to do so.]

第２の減衰装置の円板グループと中間フランジとの間に
すベシモーメントを形成するために有利には、第２の減
衰装置の軸方向に移動可能な円板が蓄力器によって軸方
向で他方の円板に向かって負荷されているとよい。従っ
て蓄力器を適切に設計することＫよって、第２の減衰装
置の滑りモーメントが変化形成されその都度の使用例に
適合させることができる。この場合、軸方向で移動可能
な円板を負荷する蓄力器がはずみ質量体に支見られてお
シ、このはずみ質量体に軸方向に不動な円板が固定され
ていることが可能である。In order to create a vesi moment between the disc group of the second damping device and the intermediate flange, it is advantageous if the axially movable disc of the second damping device is moved axially by the force accumulator. It is preferable that the load be applied toward the other disc. By suitably designing the force accumulator, the sliding moment of the second damping device can therefore be varied and adapted to the particular application. In this case, it is possible that a force accumulator loading an axially movable disk is supported on a bouncing mass, and an axially stationary disk is fixed to this bouncing mass. be.

更に有利には、蓄力器が皿ばね状の部材から構成されて
お夛、しかもこの皿ばね状の部材が外周においてスリッ
トを有しているか又は開かれており、この部材の外周が
この部材を支持するはずみ質量体のｊｌにより取囲まれ
るとよい。It is furthermore advantageous if the force accumulator is composed of a member in the form of a disc spring, and in which the disc spring-like member has a slit or is opened at its outer periphery, and the outer periphery of this member may be surrounded by a bouncy mass jl supporting .

外周においてスリットを有しているか又は関かれている
この部材は、帯材のローラ加工によって特に容易に製造
可能である。またそのような皿ばね状の部材はそれを取
囲む溝又は清白に簡単に取付は可能である。This element, which has or is surrounded by slits on its outer periphery, can be produced particularly easily by rolling the strip. Further, such a disc spring-like member can be easily attached to a groove surrounding it or in a clear manner.

更に本発明の有利な実施態様によれば、第２の減衰装置
の円板の少なくとも１つに回動防止のために設けられた
軸方拘の突起が、フランジの切欠きを貫いている。この
切欠きは有利にはフランジの外周面に配置され、場合に
よっては外方に向って開かれている。この場合特に有利
には、切欠きと突起との間に周方向で見て、第２の減衰
装置に許され九回動角度に相応する遊びが存在している
とよい。更に、個々の軸方向の突起が第２の減衰装置の
回動角度を制限するためにフランジの切欠きの輪郭に当
接するようにしてもよい。また第２の減衰装置の少なく
とも１つの円板の突起のための当付は輪郭が、フランジ
の外周に一体成形された半径方向の張出し部によって形
成されていると有利である。これＫよって第２の減衰装
置の回動角度が、その第２の減衰装置の少なくとも１つ
の円板の軸方向突起にフランジの張出し部が当付けられ
ることＫよって制限される。Furthermore, according to an advantageous embodiment of the invention, an axially restraining projection provided on at least one of the disks of the second damping device to prevent rotation passes through the recess in the flange. This recess is preferably arranged on the outer circumferential surface of the flange and is optionally open towards the outside. In this case, it is particularly advantageous if there is a play between the recess and the projection, viewed in the circumferential direction, that corresponds to the nine pivot angles allowed for the second damping device. Furthermore, it may be provided that the individual axial projections abut the contour of the recess in the flange in order to limit the rotation angle of the second damping device. It is also advantageous if the contour of the abutment for the projection of at least one disc of the second damping device is formed by a radial extension molded on the outer periphery of the flange. As a result, the rotation angle of the second damping device is limited by the fact that the projection of the flange abuts against the axial projection of at least one disc of the second damping device.

更に本発明の別の実施態様によれば、第一２の減衰装置
の円板グループに軸方向で整合する切欠きが、この円板
とフランジとの間に緊縮可能な蓄力器を受容するために
設けられていると有利である。またこの場合、蓄力器が
第２の減衰装置の回動角度の端部範囲において有効であ
ることも可能である。このような蓄力器は有利Ｋ、第２
の減衰装置の回動角度を制限するためのスト７７９体と
して役立つ。これによって、例えばフランジの張出し部
と第２の減衰装、置の両円板。According to a further embodiment of the invention, a recess axially aligned with the group of discs of the first second damping device receives a retractable force storage device between this disc and the flange. It would be advantageous if it were provided for this purpose. In this case, it is also possible that the force accumulator is active in the end range of the pivot angle of the second damping device. Such a power accumulator has an advantageous K, a second
It serves as a strike 779 body for limiting the rotation angle of the damping device. This allows for example the overhang of the flange and the second damping device, both disks of the device.

との間で、該第２減衰装置の回動角度の端部範囲におい
て激しい衝突が発生することが防がれ、延いては騒音も
回避される。更に蓄力器がコイルばね及び（又は）ゴム
ブロックによって構成されていると有利である。更にこ
の場合、蓄力器がフランジの張出し部の間に設けられて
おり、この張出し部によって直接に負荷されていると有
利である。This prevents severe collisions from occurring in the end range of the pivot angle of the second damping device, and thus also avoids noise. Furthermore, it is advantageous if the force storage device is constructed by a coil spring and/or by a rubber block. Furthermore, it is advantageous in this case if the energy storage device is arranged between the extensions of the flange and is directly loaded by these extensions.

本発明の別の極めて安価な実施態様によれば、フランジ
と第２の減衰装置の円板の）なくとも１つとの間で有効
な摩擦ライニングが、フランジの張出し部に固定された
、摩擦又は滑り材料から成る個々のセグメントから構成
されていると有利である。まだフランジが少なくとも１
つのはずみ質量体を通して同心的に案内されていると一
層有利である。According to another very inexpensive embodiment of the invention, a friction lining, which is effective between the flange and at least one of the discs of the second damping device, is fixed to the flange bulge. It is advantageous if it is constructed from individual segments of sliding material. There is still at least one flange
It is even more advantageous if it is guided concentrically through two spring masses.

更に本発明の別の有利な実施態様によれば、はずみ質量
体の少なくとも１つが他方のはずみ質量体に向かって軸
方向に延びるリング状の付加部を有し、この付加部の半
径方向内側に第２の減衰装置と第１の減衰装置とが配置
されている。またこの際Ｋ、付加部が第２の減衰装置を
軸方向で掴んでいると有利であり、即ち多くの使用例に
おいて、第２の減衰装置の軸方向に移動可能な円板を負
荷する皿ばね状の部材が、付加部の開放端部範囲に設け
られた溝内で軸方向と半径方向とに支えられていると有
利である゛。Furthermore, according to a further advantageous embodiment of the invention, at least one of the spring masses has a ring-shaped extension extending axially towards the other spring mass, radially inwardly of this extension. A second damping device and a first damping device are arranged. In this case, it is also advantageous if the extension K grips the second damping device in the axial direction, i.e. in many applications the plate which loads the axially movable disc of the second damping device It is advantageous if the spring-like element is supported axially and radially in a groove provided in the open end region of the extension.

しかしまた別の使用例のだめには、第２の減衰装置を軸
方向で掴んでいる付加部の端面の上に第２の減衰装置の
軸方向に固定された円板が固定されており、付加部を有
するはずみ質量体と前記円板との間にリング状の室が形
成されており、この室内にフランジが半径方向で突入し
ており、この室内に第２の減衰装置の軸方向に移動可能
な円板が受容されているとよい。この場合有利には、内
燃機関のクランク軸と結合された第１のはずみ質量体が
付加部を有しているとよい。この構成においては更に、
第２の減衰装置の皿ばね状の部材が第１のはずみ質量体
と第２の減衰装置の軸方向に移動可能な円板との間に緊
縮されていると有利である。However, in another example of use, a disk fixed in the axial direction of the second damping device is fixed on the end face of the attachment part that grips the second damping device in the axial direction. A ring-shaped chamber is formed between the bouncy mass having a section and the disk, into which a flange projects radially, into which the second damping device is displaceable in the axial direction. It is good if possible discs are accepted. In this case, it is advantageous if the first floating mass connected to the crankshaft of the internal combustion engine has an extension. In this configuration, furthermore,
It is advantageous if the disc spring-like element of the second damping device is compressed between the first spring mass and the axially movable disk of the second damping device.

本発明の更に別の実施態様によれば、フラン　−ジを同
心的に案内するために、該フランジの外周面に一体形成
された張出し部がはずみ質量体の軸方向の付加部に半径
方向で支えられていると有利である。この構成によって
、第１の減衰装置の機能が外部からの摩擦によって妨げ
られることが防がれる。これは特に第１の減衰装置の回
動範囲の内の、両方のはずみ質量体の間で伝達されるモ
ーメントが比較的に小さな範囲のために有利である。更
忙相応したはずみ質量体の付加部とフランジの張出し部
との間に、フランジの半径方向案内のために働く摩擦又
はすベリライニングが配置されていると有利である。According to a further embodiment of the invention, in order to guide the flange concentrically, a bulge integrally formed on the outer circumferential surface of the flange is radially attached to the axial extension of the spring mass. It is advantageous to be supported. This configuration prevents the functioning of the first damping device from being disturbed by external friction. This is advantageous in particular because of the relatively small range of rotation of the first damping device in which the moments transmitted between the two floating masses are relatively small. It is advantageous if a friction or slip lining is arranged between the extension of the corresponding spring mass and the extension of the flange, which serves for radial guidance of the flange.

またこの装置の有利な構造によれば、少ｔ（ともフラン
ジの個々の張出し部がそれぞれ、摩擦及び（又は）滑り
材料から成るキャップによって掴まれており、このキャ
ップが一方ではフランジの半径方向の案内を保証し、他
方では第２の減衰装置の間の各円板とフランジとの間に
摩擦モーメントな生せしめるために緊締されているとよ
い。この場合のキャップは有利には、−半径方向で見て
一端部範囲に弾性的に変形可能なストッパ範囲を一体に
成形され１有しており、このストン・ぞ範囲が第２の減
衰装置の回動角度を制限するためにストン・ぐと協働す
るとよい。According to an advantageous construction of the device, the individual extensions of the flanges are each gripped by a cap made of friction and/or sliding material, which on the one hand extends radially across the flange. It can be tightened to ensure guidance and, on the other hand, to create a frictional moment between the respective disc and the flange between the second damping device.The cap in this case is preferably -radially It has an integrally molded elastically deformable stop region 1 in one end region when viewed from above, and this stop region has a stop region 1 which can be adapted to limit the rotation angle of the second damping device. It's good to work together.

更に本発明の有利な実施態様によれば、フランジをセン
タリングするために少なくともフランジの個々の張出し
部が一周方向で見て一相応するはずみ質量体の軸方向の
付加部に支えられたＵ字形の案内シューにより掴まれて
おり、更にこの際にＵ字形の案内シューの側脚が第２の
減衰装置の回動遊びを制限するストッパと協働するよ５
になっている。このスト左ノξは例えば両方の円板の間
で軸線方向に延びる結合部汀文は、前述のように第２の
減衰装置の側円板の切欠き内に受容された蓄力器又は相
応したはずみ質量体の付加部に配置された当付は部によ
って形成可能である。更にＵ字形の案内シューの側脚と
フランジ°の張出し部との間Ｋ、周方向で見て遊びが存
在していると有利である。またＵ字形の案内シューの側
脚とフランジの張出し部との間に蓄力器が設けられてい
てもよい。このような蓄力器は有利には弾性的な材料−
例えばゴムから形成されているとよい、この蓄力器によ
って第２の減衰装置の端部範囲における強過ぎる当付け
が回避され、延いては騒音発生が防がれる。Furthermore, according to an advantageous embodiment of the invention, in order to center the flange, at least the individual flange of the flange is provided with a U-shaped support, viewed in the circumferential direction, which rests on an axial extension of the corresponding spring mass. It is gripped by a guide shoe, and in this case the side legs of the U-shaped guide shoe cooperate with a stop that limits the rotational play of the second damping device.
It has become. The left side of this damper ξ can be, for example, a connecting part extending axially between the two discs, which can be connected to a force accumulator or a corresponding impetus, which is received in a recess in the side disc of the second damping device, as described above. The abutment arranged on the additional part of the mass can be formed by a part. Furthermore, it is advantageous if there is a play between the side legs of the U-shaped guide shoe and the extension of the flange K, viewed in the circumferential direction. It is also possible for a power storage device to be provided between the side leg of the U-shaped guide shoe and the extension of the flange. Such a force accumulator is preferably made of an elastic material.
This energy storage device, which may be made of rubber, for example, prevents too strong a contact in the end region of the second damping device and thus prevents noise generation.

両方のはずみ質量体の間での許容回動角度を制限するた
めＫ、フランジと第２のはずみ質量体との間に第１の減
衰装置の周方向の運動を制限するストッパが設けられて
いると有利である。In order to limit the permissible rotation angle between the two bouncing masses K, a stop is provided between the flange and the second bouncing mass for limiting the circumferential movement of the first damping device. It is advantageous.

またこの際にストツノソがスペーサピンによって形成さ
れており、このスペーサピンが第１の減衰装置の円板を
相互に結合しかつ第２のはずみ質量体と結合され、フラ
ンジの切欠きを軸方向に貫いているとよい。更にこの場
合、スペーサピンがフランジの切欠きの端部範囲に当接
することＫよって第１の減衰装置の回動角度が制限され
ると有利である。またこのフランジの切欠きの構造と配
置は、該クランプが内周に半径方向の歯を有し、この歯
がスペーサピンの間に係合するように゛なっていると有
利である、更にこの歯がフランジの半径方向内側の範囲
に切欠きを設けることによって形成されているとよい。Also in this case, the suspension is formed by a spacer pin, which connects the discs of the first damping device to each other and to the second spring mass and extends the recess in the flange in the axial direction. It's good if you stick to it. Furthermore, it is advantageous in this case for the rotation angle of the first damping device to be limited by the fact that the spacer pin rests in the end region of the recess in the flange. The structure and arrangement of the recess in the flange is advantageous if the clamp has radial teeth on its inner periphery, which teeth are adapted to engage between the spacer pins; Advantageously, the teeth are formed by recesses in the radially inner region of the flange.

第１の減衰装置の両方の円板を結合するスペーサピンが
フランジの歯に当付けられることによつ【、相応するは
ずみ質量体に対するフランジの回動が制限される。The spacer pin connecting the two discs of the first damping device rests on the teeth of the flange, thereby limiting the rotation of the flange relative to the corresponding spring mass.

本発明の更に別の有利な実施態倦によれば、第２の減衰
装置の円板がスペーサ部材、例えばスペーサピンを介し
て互いに軸方向に固定されており、少なくとも円板の一
方がスペーサ部材の間に周方向に延在する弾性的に・２
イアスをかけた波状部を有し、この波状部がフランジを
他方の円板に向かって圧着している。第２の減衰装置の
この構造によれば、該第２減衰装置の両円板を相互圧着
させるた゛めの特別な蓄力器は、不要である。更にこの
構造においては、第２の減衰装置の両円板の間に配置さ
れたスペーサピンが同時に、円板を一方のはずみ質量体
に固定するためＫも働いていると有利である。According to a further advantageous embodiment of the invention, the disks of the second damping device are axially fixed to one another via a spacer element, for example a spacer pin, and at least one of the disks is provided with a spacer element. elastically extending circumferentially between ・2
It has an ias waved portion which presses the flange towards the other disc. With this construction of the second damping device, no special force accumulator is required for pressing the two discs of the second damping device together. Furthermore, it is advantageous in this construction if the spacer pin arranged between the two discs of the second damping device also serves at the same time to secure the discs to one of the floating masses.

更に本発明によれば有利には、第２の減衰装置のフラン
ジの両側に設けられた円板が周方向に分配されたＵ字形
ばね若しくはクランプでフランジに対して緊定されてい
る。この場合更に、Ｕ字形ばね若しくはクラ７ノがフラ
ンジと第２の減衰装置の両方の円板とを軸方向に掴んで
おり、半径方向に延びる脚部で円板を軸方向で背後から
掴んでおりかつフランジに向かって負荷しているとよい
。このＵ字形ばね又はクランプの脚部は半径方向内方へ
向って延びていると有利である。Furthermore, it is advantageous according to the invention if the disks on both sides of the flange of the second damping device are tensioned against the flange by means of circumferentially distributed U-shaped springs or clamps. Furthermore, the U-shaped spring or clamp 7 grips both the flange and the disk of the second damping device in the axial direction, and the radially extending leg grips the disk axially from behind. It is recommended that the load be applied toward the flange. Advantageously, the legs of this U-shaped spring or clamp extend radially inward.

更に有利な実施態様によれば、一方のはずみ質量体が軸
方向の突起を有しこの突起が第一２の減衰装置の、フラ
ンジの側面を保穫する円板の切欠きに係合し、該円板の
回動を防止する。この場合更に有利には、周方向で見て
軸方向の突起の間Ｋ、フランジの外周に一体成形された
張出し部が半径方向で係合しており、蓄力器が第２の減
衰装置の円板の切欠きに受容されており、蓄力器が第２
の減衰装置の回動角度を制限するためにフランジの張出
し部の終端ストツノぞとして用いられているとよい。更
に、π方の円板の４蓄力器を受容する切欠きが、他方の
円板の、前記切欠きに軸方向で向き合った切欠きに対し
、軸方向で向き合った切欠きに受容された蓄力器が円板
を円板の切欠きを貫く突起に対して周方向で緊定される
よ５Ｋ、周方向でずらされて−いると有利である。これ
によって騒音発生が回避される。また軸方向の突起がボ
ルト又はピンに。According to a further advantageous embodiment, one of the spring masses has an axial projection which engages in a recess in the disc of the first second damping device which protects the lateral side of the flange; Prevent rotation of the disc. In this case, it is further advantageous that between the axial projections K, viewed in the circumferential direction, a projection integrally formed on the outer periphery of the flange engages in the radial direction, so that the force accumulator is connected to the second damping device. It is received in the notch of the disk, and the energy storage device is the second one.
In order to limit the rotation angle of the damping device, it is preferable to use it as a stopper groove at the end of the overhanging part of the flange. Furthermore, the notches for receiving the four force accumulators in the π-direction disc are received in the notches facing in the axial direction with respect to the notches in the other disc facing the notches in the axial direction. It is advantageous if the force accumulator is offset in the circumferential direction by 5K such that the disk is clamped circumferentially against a projection passing through a recess in the disk. This avoids noise generation. Also, the protrusion in the axial direction can be used as a bolt or pin.

よって形成されており、このボルト又はピンが一方のは
ずみ質量体に固定されているとよい。This bolt or pin is preferably fixed to one of the spring masses.

更に本発明の有利な実施態様によ上ば、フランジが第２
の減衰装置の円板の範囲に軸方［口Ｊり切欠きを有し、
これらの切欠きに摩擦ブロック又は摩擦ライニングが受
容されており、この摩擦ブロック又は摩擦ライニングが
第２の減衰装置の円板の間に緊締されている。この際に
多くの使用例においては、前記切欠きが軸方向で貫通シ
テオリ、これらの切欠きを通してフランジの厚さよりも
大きな厚さを有する摩擦ブロックが差込まれているとよ
い。更に摩擦ブロックが切欠き内で軸方向に移動可能で
あり、しかも半径及び（又は）周方向で案内されている
と有利である。Furthermore, according to an advantageous embodiment of the invention, the flange has a second
It has an axial cutout in the range of the disc of the damping device,
Friction blocks or friction linings are received in these recesses and are clamped between the discs of the second damping device. In many applications, it is advantageous for the recesses to pass through in the axial direction and for a friction block having a thickness greater than the thickness of the flange to be inserted through these recesses. Furthermore, it is advantageous if the friction block is axially movable in the recess and is guided radially and/or circumferentially.

しかし多くの使用例忙おいては、軸一方向の切欠きに相
前後して配置された１対の摩擦ブロックが受容されてお
り、この摩擦ブロックの間に蓄力器例えば皿ばねが設け
られ、この蓄力−器が摩擦ブロックを第２の減衰装置の
円板に向がって緊定していることも有利である。更に装
置の、簡単な組立てを可能とするために有利には、摩擦
ブロックとその間に介在させられている蓄力器が結合部
材を介して軸方向でまとめられているが、結合部材が蓄
力器の作用に抗して両方の摩擦ブロックが限られた範囲
で軸方向に移動することを許すようになっているとよい
。However, in many applications, a recess in one direction of the shaft receives a pair of friction blocks arranged one after the other, between which a force accumulator, for example a disc spring, is arranged. It is also advantageous that this force accumulator tensions the friction block towards the disc of the second damping device. Furthermore, in order to enable a simple assembly of the device, it is advantageous if the friction block and the force accumulator interposed between them are joined together in the axial direction via a coupling element, which Advantageously, both friction blocks are allowed to move within a limited range in the axial direction against the action of the device.

更に第２の減衰装置内に摩擦ブロックを配設する構造に
おいて一層有利には、フランジが軸方向で向き合った袋
孔な、摩擦ブロックを受容するために有しており、フラ
ンジが軸方向で互いに向き合った２つの袋孔の間にある
中間壁に、切欠きを有し、との切欠きを通って軸方向で
向き合った摩擦ブロックを結合する結合ぎンぷ貫通して
おり、少なくとも一方の摩擦ブロックと中間壁との間に
蓄力器、例えば皿ばねが配置されておりこの蓄力器が摩
擦ブロックを第２の減衰装置の円板の間で緊定しており
、結合部材が互いに向き合った摩擦ブロックが蓄力器の
作用に抗して軸方向で限られた移動を行なうことを可能
にするとよい。Furthermore, it is particularly advantageous in the arrangement of the friction blocks in the second damping device that the flanges have axially opposed blind holes for receiving the friction blocks, the flanges axially facing each other. The intermediate wall between the two opposed blind holes has a notch, through which the connecting gimp connecting the axially opposed friction blocks passes through, and at least one of the friction A force accumulator, for example a disk spring, is arranged between the block and the intermediate wall, which force accumulator tensions the friction block between the discs of the second damping device, and the coupling members are frictionally opposed to each other. It is advantageous if the block is allowed to carry out a limited movement in the axial direction against the action of the force accumulator.

更に本発明の実施態様によれば、第１の減衰装置が第２
の減衰装置の半径方向内側に設けられていると有利であ
る。Further in accordance with an embodiment of the invention, the first damping device is coupled to the second damping device.
Advantageously, the damping device is arranged radially inside the damping device.

次に図面について本発明を説明する：第１図と＠２図に示された回転衝撃を補償するための装
置１は２つのはずみ質量体３，４に分割されたはずみ車
２を有している。第１のはずみ質量体３け図示されてい
ない内燃機関のクランク軸５の上に固定ねじ６を介して
固定されている。第２のはずみ質量体生の上には摩擦ク
ラッチ７が図示されていない手段を介して固定されてい
る。摩擦クラッチ７の圧力板８とはずみ質量体牛との間
にはクラッチ円板９が設けられている。このクラッチ円
板９は図示されていない伝動装置の入力軸１０に受容さ
れている。The invention will now be explained with reference to the drawings: The device 1 for compensating rotational shocks shown in FIGS. 1 and 2 has a flywheel 2 divided into two flywheel masses 3, 4. . Three first bouncing masses are fastened via fixing screws 6 onto a crankshaft 5 of an internal combustion engine (not shown). A friction clutch 7 is fixed on the second spring mass by means not shown. A clutch disc 9 is provided between the pressure plate 8 of the friction clutch 7 and the spring mass. This clutch disc 9 is received in an input shaft 10 of a transmission (not shown).

摩擦クラッチ７の圧力板８ははずみ質量休養に向かって
、クラッチカバー１１に旋回可能に支承された皿ばね１
２によって負荷されている。The pressure plate 8 of the friction clutch 7 is mounted on a disc spring 1 pivotably mounted on the clutch cover 11 towards the rest of the spring mass.
2.

摩擦クラッチ７を作動することによってはずみ質量体牛
、ひいてははずみ車２は伝動装置の入力軸１０に接続さ
れかつ遮断される。はずみ質量体さとはずみ質量体牛と
の間には第１の減衰装置１３とこの減衰装置１３と直列
的に配置された第２の減衰装置１４が設けられている。By activating the friction clutch 7, the flywheel mass and thus the flywheel 2 are connected to and disconnected from the input shaft 10 of the transmission. A first damping device 13 and a second damping device 14 arranged in series with this damping device 13 are provided between the spring mass and the spring mass.

この減衰装置１４ははずみ質量体３，４との間の限られ
た相対回動を可能にする。This damping device 14 allows a limited relative rotation between the spring masses 3, 4.

両方のはずみ質量体３，４は互いに相対的に軸受１５を
介して回動可能に支承されている。The two spring masses 3, 4 are rotatably supported relative to one another via bearings 15.

軸受１５は分割された内レース１７を有する複列のアン
ギュラ形ころがり軸受１６である。このアンギュラ形こ
ろがり軸受１６の外レース１６ａははずみ質量体生の孔
１８に配置され、分割された内レース１７ははずみ質量
体３の中心からクランク軸５とは反対側に軸方向に延び
る円筒形のピン１９の上に配置されている。The bearing 15 is a double row angular rolling bearing 16 with a split inner race 17. The outer race 16a of this angular roller bearing 16 is arranged in the bore 18 of the spring body, and the divided inner race 17 has a cylindrical shape extending axially from the center of the spring mass 3 to the side opposite to the crankshaft 5. It is arranged on the pin 19 of.

内レース１７の両方のレース部分−１７−ａ、１７ｂは
皿ばね２０の形をした蓄力器によっ゛て柚゛方向に緊定
されている。レース部分１７ｂをピン１９の端面１９ａ
の上に確保するためには確保円板２１がねじ２１ａで固
定されている。この確保円板２１は半径方向外方へピン
１９を越えて延びており、レース部分１７ｂを軸方向で
支えている。レース部分１７ａとはずみ質量体３との間
に配置された皿ばね２０はレース部分１７ａを軸方向で
レース部分１７ｂに向かって負荷している。この場合に
は皿ばね２０は半径方向外側の範囲ではずみ質量体３に
支えられ、半径方向内側の範囲でレース部分１７ａに作
用する。このような構造でアンギュラ形こ−ろがり軸受
１６の転動体はそれに配属された転動−路の間で緊縮さ
れる。摩擦クラッチ７を作動した場合にもアンギュラ形
ころがり軸受１６が緊定−されたままにとどめられるよ
うに皿ばね２０は摩擦クラッチ７を作動するために必要
な最大力よりも大きい力を生ぜしめる。有利であるのは
皿ばね２０によって生ぜしめられた力が少なくともほぼ
摩擦クラッチ７を解離させるために必要な最大力の２倍
の大きさを有するように選ばれていることである。The two race parts 17-a, 17b of the inner race 17 are tensioned in the vertical direction by a force accumulator in the form of a disc spring 20. The race portion 17b is attached to the end surface 19a of the pin 19.
A securing disk 21 is fixed with screws 21a to secure it above. This securing disk 21 extends radially outwardly beyond the pin 19 and supports the race portion 17b in the axial direction. A disc spring 20 arranged between the race part 17a and the spring mass 3 loads the race part 17a axially towards the race part 17b. In this case, the disk spring 20 rests on the spring mass 3 in its radially outer region and acts on the race part 17a in its radially inner region. With this construction, the rolling elements of the angular rolling bearing 16 are compressed between the rolling tracks assigned to them. The disk spring 20 produces a force greater than the maximum force required to actuate the friction clutch 7, so that the angular roller bearing 16 remains tensioned even when the friction clutch 7 is actuated. Advantageously, the force exerted by disk spring 20 is selected to have at least approximately twice the maximum force required to disengage friction clutch 7.

はずみ質量体３は半径方向外側に軸方向のリング状の付
加部２２を有している。この付加部２２は室２３を形成
し、この室２３内には第１の減衰装置１３と第２の減衰
装置１４とが受容されている。減衰装置１４の入力部は
円板グループ、すなわちはずみ質量体３と回動−不能で
ある。互いに軸方向に間隔をおいた２つの円板２４．２
５によって形成されている。リング状の円板２５は付加
部２２の端面２２ａにリベット２６で固定されかつ内側
にある範囲２５ａで室２３を軸方向で制限している。室
２３に受容された円板２４は外周部に一体に成形された
舌状部２４ａによって形成された軸方向の突起を有して
いる。円板２４を円板２５に対して回動防止するために
は舌状部２４ａは円板２５の切欠き２７に係合する。切
欠き２７と舌状部２４ａは１円板２５に対して円板２４
が軸方向に移動できるように構成されている。両方の円
板２４と２５との間にはフランジ２９０半径方向の張出
し部２８が軸方向で緊締されている。このためには軸方
向で円板２４−゛とはずみ質量体３との間に設けられた
皿ばね３０の形をした蓄力器が円板２４を円板２５に向
かって負荷している。The spring mass 3 has an axial ring-shaped extension 22 on the radially outer side. This extension 22 forms a chamber 23 in which a first damping device 13 and a second damping device 14 are received. The input part of the damping device 14 is non-rotatable with respect to the disk group, ie the spring mass 3. Two discs 24.2 axially spaced from each other
It is formed by 5. A ring-shaped disc 25 is fixed to the end face 22a of the additional part 22 with a rivet 26 and limits the chamber 23 in the axial direction with an inner region 25a. The disc 24 received in the chamber 23 has an axial protrusion formed by an integrally molded tongue 24a on its outer periphery. In order to prevent the disk 24 from rotating relative to the disk 25, the tongue 24a engages with a notch 27 in the disk 25. The notch 27 and the tongue-shaped portion 24a are arranged on the disc 24 for one disc 25.
is configured to be movable in the axial direction. A radial extension 28 of a flange 290 is axially clamped between the two discs 24 and 25. For this purpose, a force accumulator in the form of a disc spring 30, which is arranged axially between the disc 24-' and the spring mass 3, loads the disc 24 towards the disc 25.

このためには皿ばね３０は半径方向外側の範囲ではずみ
質量体３に支えられかつ半径方向内側　−の範囲で円板
２４に支えられている。皿ばね３０の外周部は開いてい
るかもしくはスリットを有している。すなわち皿ばね３
０のリング状の基体は１個所で切離されており１皿ばね
３ｏは半径方向外側の外周部ではずみ質量体３のリング
状の肩３１に半径方向で支えられている。フランジ２９
の張出し部２８と両方の円板２４゜２５との間にはそれ
ぞれ摩擦ライニングが設けられている。この摩擦ライニ
ングは張出し部２８に接着された個々のライニングセグ
メント３２から構成されている。フランジ２９の張出し
部２８０間では円板２４．２５に切欠き３３゜３４が設
けられ、これらの切欠き３３　、３．、、−４は軸方向
で互いに整合しておりかつ蓄力器３５を受容している。For this purpose, the disc spring 30 is supported in its radially outer region on the spring mass 3 and in its radially inner region on the disc 24. The outer periphery of the disc spring 30 is open or has a slit. In other words, disc spring 3
The ring-shaped base body 0 is separated at one point, and the disc spring 3o is radially supported on the ring-shaped shoulder 31 of the spring mass 3 at its radially outer outer circumference. Flange 29
A friction lining is provided between the bulge 28 and the two discs 24, 25, respectively. This friction lining is made up of individual lining segments 32 glued to the overhang 28. Between the overhangs 280 of the flange 29, cutouts 33.34 are provided in the disc 24.25, and these cutouts 33,3. , , -4 are axially aligned with each other and receive the force accumulator 35.

図示の実施例ではこの蓄力器はコイルばね３５によって
形成されているが、しかし硬質ゴムばねを使用すること
もできる。蓄力器３５はフランジ２９の張出し部２８の
ためのリミットストッ／ξとして役立ち、これによって
第２の減衰装置１４の回動角度を制限する。In the embodiment shown, this energy store is formed by a helical spring 35, but it is also possible to use a hard rubber spring. The force accumulator 35 serves as a limit stop /ξ for the extension 28 of the flange 29 and thus limits the rotation angle of the second damping device 14 .

蓄力器３５の減衰作用によって、減衰装置１４の回動角
度の端部範囲で硬い衝突が、回避てれる。。Due to the damping effect of the force accumulator 35, hard collisions are avoided in the end range of the pivot angle of the damping device 14. .

減衰装置１４が中間位置で示さｎている第２図から特に
解るように、蓄力器３５と張出し部２８との間には遊び
３６＋３６８が存在している。この遊び３６＋３６８は
蓄力器３５が圧縮される値だけ拡大されて、減衰装置１
４の出力部を形成する張出し部２８と入力部を形成する
円板２４との間に許す回動角を規定する。As can be seen in particular from FIG. 2, in which the damping device 14 is shown in an intermediate position, there is a play 36+368 between the energy storage device 35 and the extension 28. This play 36+368 is expanded by the amount by which the force accumulator 35 is compressed, and the damping device 1
The rotation angle allowed between the overhanging part 28 forming the output part of No. 4 and the disc 24 forming the input part is defined.

減衰装置１４の出力部を形成するフランジ２９は第１の
減衰装置１３の入力部を同時に形成している。第１の減
衰装置１３は會の円板グループ、すなわちフランジ２９
０厩側に配置された２つの円板３７．３８を有している
。この円板３７．３８はスペーサピン３９を介して軸方
向の間隔をおいて互いに回動不能に結合されかつはずみ
質量体４に枢着されている。両方の円板３７．３８は半
径方向外側で減衰装置１４のリング状の円板２４．２５
によって取囲まれている。さらに図示の実施例では円板
３７と２４及び３８と２５は少なくともほぼ同一平面内
に配置されている。円板３７と３８とフランジ２９の張
出し部２８の半径方向内側の範囲には切欠き３７ａ、３
８ａと２９ａとが設けられ、これらの切欠き３７ａ、３
８ａ、２９ａ内にはコイルばね４０の形をした蓄力器が
収容て′れている。蓄力器４０はフランジ２９と両方の
円板３７．３８との間の相対回動に抗して作用す−る。The flange 29 forming the output of the damping device 14 simultaneously forms the input of the first damping device 13 . The first damping device 13 is a group of discs, namely the flange 29
It has two discs 37 and 38 placed on the 0-stair side. The disks 37, 38 are fixedly connected to one another at an axial distance via spacer pins 39 and are pivotally connected to the spring mass 4. Both discs 37, 38 are connected radially outwardly to the ring-shaped disc 24, 25 of the damping device 14.
surrounded by. Furthermore, in the illustrated embodiment, the disks 37 and 24 and 38 and 25 are arranged at least approximately in the same plane. Notches 37a, 3 are provided in the radially inner range of the discs 37 and 38 and the overhanging portion 28 of the flange 29.
8a and 29a are provided, and these notches 37a, 3
A power accumulator in the form of a coil spring 40 is accommodated in 8a, 29a. The force accumulator 40 acts against the relative rotation between the flange 29 and the two disks 37,38.

さら罠第１の減衰装置１３は摩擦装置１３ａを有し、こ
の摩擦装置１３ａは両方のはずみ質量体３，４の間に与
えることのできる総回動角度に亘って有効である。The counterbalance first damping device 13 has a friction device 13a which is effective over the total rotational angle that can be applied between the two spring masses 3, 4.

摩擦装置１３ａは軸方向で円板３７とはずみ質量体３と
の間に配置され、皿ばねによって形成された蓄力器４１
を有している。この蓄力器４１は円板２７と圧力リング
４２との間に緊締されて保持され、これによって圧力リ
ング４２とはずみ質量体３との間に配置された摩擦リン
グ４３が締込まれる。蓄力器４１によって円板３７に生
ぜしめられた力は軸受１５を介して受止められる。圧力
リング４２は張出し部４２８を備えており、この張出し
部４２８はリベット３９のヘッドを掴んでおり、こｎに
よって圧力板ははずみ質量体Φと回動不能に結合される
。The friction device 13a is arranged axially between the disk 37 and the spring mass 3 and has a force accumulator 41 formed by a disc spring.
have. This force accumulator 41 is held tightly between the disk 27 and the pressure ring 42, which forces a friction ring 43 arranged between the pressure ring 42 and the spring mass 3. The force generated in the disc 37 by the force accumulator 41 is received via the bearing 15. The pressure ring 42 is provided with a bulge 428 which grips the head of the rivet 39, whereby the pressure plate is fixedly connected to the spring mass Φ.

フランジ２９は半径方向外側の外周部に内側に開いた切
欠き４４を有し、この切欠き４４を通してスペーサピン
３９が軸方向に突出する。The flange 29 has an inwardly open notch 44 on its radially outer circumference, through which the spacer pin 39 projects in the axial direction.

この切欠きは半径方向内側に向いた歯４５を形成する。This notch forms a radially inwardly directed tooth 45.

この歯４５は一周方向で見て一スヘーサピン３９の間に
係合し、このスペーサピン３９と第１の減衰装置１３の
角度変位を制限するために協働する。This tooth 45 engages between one spacer pin 39 in the circumferential direction and cooperates with this spacer pin 39 to limit the angular displacement of the first damping device 13 .

両方の円板３７．３８の切欠き３７　ａ　、　３８ａと
フランジ２９の切欠き２９ａとその内部に設けられたコ
イルばね４０は第１の減衰装置１３の外周に亘って多段
の減衰特性線が形成されるような寸法を有しかつ配置さ
れている。The notches 37a and 38a of both discs 37 and 38, the notch 29a of the flange 29, and the coil spring 40 provided therein form a multistage damping characteristic line over the outer periphery of the first damping device 13. It is sized and arranged as follows.

フランジ２９を回転軸線４７に対してかつはずみ質量体
３，４に対してほぼ同心的に案内するためには、フラン
ジ２９は半径方向の張出し　一部２８ではずみ質量体３
の軸方向の付加部２２の内周面２２ｂに支えられる。In order to guide the flange 29 approximately concentrically with respect to the axis of rotation 47 and with respect to the spring masses 3, 4, the flange 29 has a radial overhang.
It is supported by the inner circumferential surface 22b of the additional portion 22 in the axial direction.

図示の実施例の装置は、第２図に示された不作用位置か
ら、モーメントの変化が生じた場合にまず第１のはずみ
質量体３が円板グループ２斗、２５とフランジ２９と一
緒に第２のはずみ質量休養と円板グループ３７．３８と
に対してばね４０の作用に抗して回動させられる。この
場合にはフランジ２９と円板グループ３７．３８とにお
ける窓開口が異なる大きさを有していることに基づいて
減衰作用が次第に上昇させられる。この相対回動はばね
４０の緊縮によって生ぜしめられた回転モーメントが第
２の減九装置１４によって伝達可能な摩擦モーメントに
達するまで行なわれる。この方向での相対運動が進行す
る間に第２の減衰装置がスリップを開始する。この場合
にはばね３５が張出し部２８の側面に当接するまでは第
２のはずみ質量体に対するフランジ２９の相対回動は行
なわれない。張出し部２８はフランジ２９が第１のはず
み質量体３と一緒に第２のはずみ質量休養に対して相対
運動することを許す。この場合に、はぼねは歯４５がピ
ン３９に当接するまで圧縮させられる。The device of the illustrated embodiment is such that, from the inactive position shown in FIG. It is rotated against the action of the spring 40 against the second spring mass rest and the disk group 37,38. In this case, the damping effect is gradually increased due to the different sizes of the window openings in the flange 29 and the disk groups 37, 38. This relative rotation takes place until the rotational moment produced by the tensioning of the spring 40 reaches a frictional moment that can be transmitted by the second reduction device 14. While the relative movement in this direction is progressing, the second damping device begins to slip. In this case, no rotation of the flange 29 relative to the second spring mass takes place until the spring 35 comes into contact with the side surface of the flange 28. The flange 28 allows the flange 29 to move relative to the rest of the second bouncing mass 3 together with the first bouncing mass 3. In this case, the spring is compressed until the tooth 45 abuts the pin 39.

特に第２図から解かるように図示された実施例では張出
し部２８ｔ′ｉ、第２の減衰装置１４の最大回動角度を
制限するために張出し部２８がばね３５に当接するよう
に構成されている。しかし張出し部２６のストッパ輪郭
を適当に変化させることによって付加的に舌状部２４ａ
を関与させることもできる。このような実施例では張出
し部２８の各ストッパ輪郭は蓄力器３５と舌状部２４ａ
とに対して一周方向で現て一蓄力器３５がまず回転衝撃
を受止め１．ついで舌状部２４ａと一緒に両方の円板２
４．２５とフランジ２９との間の回動を制限するように
構成する必要がある。さらに蓄力器３５を省略し、舌状
部２４ａだけを第２の減衰装置の入力部と出力部との間
の回動角度を制限するために関与させることも可能であ
る。In the illustrated embodiment, as can be seen in particular from FIG. ing. However, by suitably varying the stopper profile of the overhang 26, the tongue 24a can be additionally
can also be involved. In such an embodiment, each stop contour of the bulge 28 is connected to the force accumulator 35 and the tongue 24a.
The force accumulator 35 first receives the rotational impact in the circumferential direction with respect to 1. Then both discs 2 together with the tongue 24a
4.25 and the flange 29 must be configured to limit rotation. Furthermore, it is also possible to omit the force accumulator 35 and to involve only the tongue 24a in order to limit the rotation angle between the input part and the output part of the second damping device.

第３図に示された実施例においては、第１のはずみ質量
体１０３とリベット結合部１２６を介して回転不能罠結
合された円板１２５が半径方向外側に成形された、軸方
向に延びる舌状部１２５ａを有している。舌状部１２５
ａは第２のはずみ質量体１０４に向って延び、−円板１
２生の外周部に設けられた切欠き１２７内、に係合する
。切欠き１２７と舌状部１２５ａは円板１２４が円板１
２５に対して周方向で固定さ−れているが、しかし軸方
向では後調節の可能性を有するように互いに調和させら
れている。第２の減衰装置１１４の入力部を形成する円
板１２４と１２５との間には、第２の減衰装置１１４の
出力部を形成するフランジ１２９が締込まれている。フ
ランジ１２９と円板１２４．１２５との間にはそれぞれ
１つの摩擦ライニング１３２が配置されている。フラン
ジ１２９は第１の減衰装置１１３の入力部を同時に形成
する−０この第１の減衰装置１１３の出力部はスペーサ
ピン１３９を介して互いにかつはずみ質量体１０４と回
動不能に結合された２つの円板１３７，１３６によって
形成されている。第２の減！装置１１４と第１の減衰装
置１１３ははずみ質量体１０３の軸方向の付加部１２２
の内周面のｆ径方向内側に配置されている。付加部１２
２の自由端部には溝１３１が形成され、この溝１３１に
は皿ばね１３０が半径方向と軸方向とに支えられている
。この皿ばね１３０は取付は状態を良くするために外周
部にスリットを有しているか又は開かれている。皿ばね
１３０は半径方向内側の範囲で円板１２４を軸方向で円
板１２５に向かって負荷し、これによってフランジ１２
９が両方の円板１２４．１２５の間で軸方向に締込まれ
ており、摩擦ライニング１３２とフランジとの間の軸方
向の力と摩擦値とを介して第２の減衰装置の伝達可能な
滑りモーメントを規定する。In the embodiment shown in FIG. 3, the disc 125, which is non-rotatably trap-connected to the first bouncy mass 103 via a riveted connection 126, has an axially extending tongue shaped radially outwardly. It has a shaped portion 125a. Tongue 125
a extends towards the second bouncy mass 104, - disk 1
It engages in a notch 127 provided on the outer periphery of the second sleeve. The notch 127 and the tongue-shaped portion 125a are arranged so that the disc 124 is connected to the disc 1.
25 in the circumferential direction, but in the axial direction they are matched to each other with the possibility of later adjustment. A flange 129, which forms the output part of the second damping device 114, is fitted between the discs 124 and 125, which form the input part of the second damping device 114. A friction lining 132 is arranged between the flange 129 and the discs 124, 125 in each case. The flange 129 simultaneously forms the input of the first damping device 113 - the output of this first damping device 113 is connected via spacer pins 139 to each other and to the spring mass 104 in a non-rotatable manner. It is formed by two discs 137 and 136. Second decrease! The device 114 and the first damping device 113 are connected to the axial addition 122 of the spring mass 103.
It is arranged on the inside in the f radial direction of the inner circumferential surface of. Additional part 12
A groove 131 is formed in the free end of 2, in which a disc spring 130 is supported in the radial and axial directions. This disc spring 130 has a slit or is opened on the outer periphery in order to improve the mounting condition. The disc spring 130 loads the disc 124 axially towards the disc 125 in the radially inner region, thereby causing the flange 12
9 is axially clamped between the two discs 124, 125, and the transmission of the second damping device is possible via the axial force and the friction value between the friction lining 132 and the flange. Define the sliding moment.

第４図と第５図に示された実施例においては。In the embodiment shown in FIGS. 4 and 5.

第２の減衰装置２１４ははずみ質量体２０３の軸方向の
付加部２２２の内周面２２２ｂとフランジ２２９の張出
し部２２８との間に対応摩擦ライニング２４８が配置さ
ｎている。この対応摩擦ライニング２４８によってフラ
ンジ２２９ははずみ質量体２０３に対して同心的に案内
され゛る。対応摩擦ライニング２４８は図示された実施
例ではキャップ２４９の底を成している。The second damping device 214 has a corresponding friction lining 248 arranged between the inner circumferential surface 222b of the axial addition 222 of the spring mass 203 and the extension 228 of the flange 229. By means of this corresponding friction lining 248 the flange 229 is guided concentrically relative to the spring mass 203. A corresponding friction lining 248 forms the bottom of the cap 249 in the illustrated embodiment.

このキャップ２４９は張出し部２２８の上に載設されて
張出し部２２８を掴んでいる。キャップ２４９の側方範
囲２５０．２５１はフランジ２２９の張出し部２２８と
フランジ２２９０両　側に配置された第２の減衰装置２
１４の円板２２４．２２５との間に軸方向で緊締されて
摩擦モーメントを生ぜしめる。この軸方向の緊締力は皿
ばね２３２によって与えられる。皿ばね２３２は円板２
２５を軸方向で負荷しかつはずみ質量体２０３に軸方向
で支えられている。キャップ２４９を遠心力の作用に抗
して半径方向に確保するためには側方範囲２５０．２５
１は張出し部２２８に面した側に円弧状の隆起部２５０
ａ、２５１ａを有している。この隆起部２５０ａ　、２
５１　ａは張出し部２２８の対応する円弧状の溝２５２
に係合する。キャップ２４９をその固有弾性に基づき張
出し部２２８に被せ嵌めることを可能にするためには一
周方向で見て一隆起部２５０ａ　、２５１　ａは張出し
部２２８若しくは溝２５２の寸法の１部分に亘ってしか
延在していない。キャップ２４９の周方向で見た範囲２
５３．２５４は弾性的なもしくは緩衝作用を有する接触
範囲を形成している。この接触範囲は第２の減衰装置２
１４の回動角度を制限するためにはずみ質量体２０３と
回動不能で６るストッパ２５５と協働する。ストッパ２
５５はピン又はボルトによって形成され−ｃｔ／″する
。このピン又はボルトははずみ質量体２０３に苛１−さ
れかつ円板２２４．２２５の回動を防止するために円板
２２４．２２５を軸方向に貫通する。This cap 249 is placed on the overhang 228 and grips the overhang 228. The lateral areas 250, 251 of the cap 249 are connected to the overhang 228 of the flange 229 and the second damping device 2 arranged on both sides of the flange 2290.
14 discs 224, 225, and are tightened in the axial direction to create a frictional moment. This axial tightening force is provided by a disc spring 232. The disc spring 232 is a disc 2
25 is axially loaded and axially supported by a bouncing mass 203. In order to secure the cap 249 radially against the action of centrifugal forces, the lateral area 250.25
1 has an arcuate raised portion 250 on the side facing the overhanging portion 228;
a, 251a. This raised portion 250a, 2
51 a is a corresponding arcuate groove 252 of the overhanging portion 228;
engage with. In order to make it possible to fit the cap 249 over the overhanging portion 228 based on its inherent elasticity, the raised portions 250a and 251a only extend over a portion of the dimension of the overhanging portion 228 or the groove 252 when viewed in the circumferential direction. Not extended. Range 2 seen in the circumferential direction of the cap 249
53.254 form an elastic or damping contact area. This contact area is the second damping device 2
A non-rotatable stop 255 cooperates with the bouncing mass 203 to limit the rotation angle of 14. Stopper 2
55 is formed by a pin or bolt ct/'' which is pressed against the spring mass 203 and axially pushes the disc 224.225 to prevent rotation of the disc 224.225. penetrate through.

第６図に示された実施例においてはフランジ３２９をは
ずみ質量体３０３に対してセンタリングするためにフラ
ンジ３２９の張出し部３２８の上にＵ字形の案内シュー
３４９が設けられている。この案内シュー３４９は張出
し部材３２８を掴んでおり、案内シュー３４９の半径方
向に延びる側脚部３５３．３５４は第２の減衰装置３１
４の回動角を制限するためにはずみ質量体３０３と回動
不能であるストッパ３５５と協働する。第４図と第５図
に示された一実施例の場合のようにストッパ３５５はは
ずみ質−量体３０３に固着されかつ第２の減衰装置３１
４の。In the embodiment shown in FIG. 6, a U-shaped guide shoe 349 is provided on the overhang 328 of the flange 329 for centering the flange 329 with respect to the spring mass 303. This guide shoe 349 grips the outrigger 328 , and the radially extending side legs 353 , 354 of the guide shoe 349 support the second damping device 31 .
A non-rotatable stop 355 cooperates with the bouncing mass 303 to limit the rotation angle of 4. As in the embodiment shown in FIGS. 4 and 5, the stop 355 is fixed to the fly mass 303 and the second damping device 31
4.

フランジ３２９の両側に配置された円板を軸方向に貫く
ピンもしくはボルトによって形成されている。案内シュ
ー３４９の両方の脚部３５３と３５４とを結合する範囲
３４９ａははずみ質量体３０３の軸方向の付加部３２２
と張出し部３２８の半径方向外側の周面との間で案内さ
れている。案内シュー３４９は周方向で見て張出し部３
２８よりも大きな寸法を有している。従って張出し部３
２８の両側では張出し部３２８と案内シュ−３４９０側
脚３５３．３５４との間に遊びＸが存在している。遊び
Ｘによって形成された空間圧は硬質ゴムブロック３５７
＋７）形をした蓄力器が設けられている。この硬質ゴム
ブロック３５７は側脚３５３．３５４とストッパ３５５
との間の衝撃の減衰を行なう。案内シュー３４９は金属
又は摩擦又は滑り材料から形成することができる。It is formed by pins or bolts that axially pass through disks disposed on both sides of the flange 329. The area 349a connecting the two legs 353 and 354 of the guide shoe 349 is the axial extension 322 of the spring mass 303.
and the radially outer circumferential surface of the overhang portion 328. The guide shoe 349 is located at the overhanging portion 3 when viewed in the circumferential direction.
It has dimensions larger than 28. Therefore, the overhang 3
On both sides of 28, there is a play X between the bulge 328 and the side legs 353, 354 of the guide shoe 3490. The space pressure created by the play X is the hard rubber block 357
+7) A shaped energy storage device is provided. This hard rubber block 357 has side legs 353 and 354 and a stopper 355.
Attenuates the impact between the Guide shoe 349 can be formed from metal or friction or sliding material.

第７図と第８図においては両方の円板４２４゜４２５は
スペーサピン４５５の形をしたスペーサ部材によって相
互にかつはずみ質量体４０３と固定的に結合されている
。両方の円板４２４゜４２５の間にはフランジ４２９の
半径方向の張出し部４２８が係合している。この場合に
は張出し部４２８と両方の円板４２４．４２５との間に
は摩擦ライニング４３２が設けられている。In FIGS. 7 and 8, the two discs 424, 425 are fixedly connected to each other and to the spring mass 403 by spacer elements in the form of spacer pins 455. A radial extension 428 of a flange 429 engages between the two disks 424, 425. In this case, a friction lining 432 is provided between the bulge 428 and the two disks 424, 425.

第８図から判るように１円板４２５はスペーサピン４５
５の固定孔４５５ａの間に周方向に延びる波状部４２５
ａを有している。この波状部４２５ａは第７図から一判
るＩうに円板４２５が取付けられた状態でバイアスがか
けられる。As can be seen from FIG. 8, one disk 425 has a spacer pin 45.
A wavy portion 425 extending in the circumferential direction between the fixing holes 455a of No. 5
It has a. This corrugated portion 425a is biased with the disk 425 attached as shown in FIG.

このバイアスに基いてフランジ４２９ｆｒＬ＜はその張
出し部４２８は円板４２４．４２５の間で締込まれ、相
対運動に際して摩擦モーメントを生ぜしめる。第２の減
衰装置４１４０回動角度を制限するためには円板４２４
．４２５の切欠き内には蓄力器４３５が設けられている
。この蓄力器４３５にフランジ４２９の張出し部牛２８
が接触させられる。Due to this bias, the projecting portion 428 of the flange 429frL< is squeezed between the disks 424, 425, creating a frictional moment during relative movement. A disk 424 is used to limit the rotation angle of the second damping device 4140.
．． A power accumulator 435 is provided within the notch 425. The overhang portion 28 of the flange 429 is attached to this energy storage device 435.
is brought into contact.

第９図から第１１図に示された実施例においては、第２
の減衰装置５１４の、フランジの両側に設けられた円板
５２４．５２５は、周方向に分配されたＵ字形ばね若し
くはばねクランプ５３０によってフランジ５２９に摩擦
リング５３２を介して緊定される。Ｕ字形ばね若しくは
ばねクランプ５３０はフランジ５２９と両方の円板５２
４、５２６を軸方向に掴み、半径方向内側に向けられた
ばね脚部５３０ａ　、５３０ｂで円板５２４．５２５を
負荷する。円板５２４゜５２５の回動を防止するために
ははずみ質量体５０３にピン５５５の形の軸方向の突起
が設けられている。この突起は軸方向で円板５２４゜５
２５の対応する孔５５５ａ、５５５ｂｔ−Ｊｊ通する。In the embodiment shown in FIGS. 9 to 11, the second
The discs 524, 525 of the damping device 514 on both sides of the flange are tensioned via a friction ring 532 on the flange 529 by means of circumferentially distributed U-shaped springs or spring clamps 530. A U-shaped spring or spring clamp 530 has a flange 529 and both discs 52.
4, 526 axially and load the discs 524, 525 with the radially inwardly directed spring legs 530a, 530b. In order to prevent rotation of the disks 524.degree. 525, the spring mass 503 is provided with an axial projection in the form of a pin 555. This protrusion is a disk 524°5 in the axial direction.
25 corresponding holes 555a, 555bt-Jj.

円板５２４．５２５Ｋｒｉ蓄力器５３５を受容するため
の切欠き５３３．５３４が設けられている。この蓄力器
５３５は第２の減衰装置５゜１４０回動角度を制限する
ためにフランジ５２９の張出し部５２８と協働する。Recesses 533,534 are provided for receiving disks 524,525Kri energy accumulators 535. This energy store 535 cooperates with the bulge 528 of the flange 529 in order to limit the rotation angle of the second damping device 5° 140.

第１０図から判るように１円板５２４、５２６が組立ら
れた状態で円板５２４の切欠き５３３は円板５２５の切
欠き５３４に対して周方向で値Ｙだけずらされている。As can be seen from FIG. 10, when the disks 524 and 526 are assembled, the notch 533 of the disk 524 is offset by a value Y in the circumferential direction with respect to the notch 534 of the disk 525.

これによって蓄力器５３５は円板５２４．５２５の間で
片側だけで若しくは非対称的に軸方向に緊縮される。蓄
力器５３５の非対称的な緊縮によって円板５２４゜５２
５は孔５５５ａ、５５５ｂを通ってｆ通するピン５５５
に対して周方向に緊定される。この緊定によって第２の
減衰装置５１４の機能が著しく改善される。何故ならば
この緊定によって遊び１例えば円板５２４．５２５の孔
５５５ａ。As a result, the force accumulator 535 is compressed axially between the disks 524, 525 only on one side or asymmetrically. Due to the asymmetrical tightening of the force storage device 535, the disk 524°52
5 is a pin 555 that passes through holes 555a and 555b.
It is tightened in the circumferential direction against. This tightening significantly improves the functioning of the second damping device 514. This is because this tightening reduces the play 1, for example the holes 555a in the discs 524, 525.

５５５ｂとピン５５５との間の遊びが補償されるので、
相対回動に際して常に減衰作用が存在することになるか
らであります。Since the play between 555b and pin 555 is compensated for,
This is because there is always a damping effect during relative rotation.

第１１図に示された第２の減衰装置６°１４の実施例で
はフランジ６２９は第２の減衰装置６１４の入力部を形
成する円板６２４．６２５の間の範囲に互いに軸方向に
整合された袋孔６５６．６５７を有している。この袋孔
６５６　、６５７内にはそれぞれ１つの円板状の摩−擦
ライニング６５８．６５９が受容されている。・フラン
ジ６２９の１両方の袋孔６５８、６５７の間にある中間
壁６６０は切欠き６６１を有し、−この切欠き６６１を
リベット６６２の形をした結合部材が貫通している。こ
の結合部材は軸方向で向き合った摩擦ライニング６５８
，６５９を軸方向で結合している。軸方向で見て摩擦ラ
イニング６５８と中間壁６６０との間には緊縮された皿
ばね６６３が設けられている。この皿ばね６６３は両方
の摩擦ライニング６５８と６５９との軸方向の拡開若し
くは軸方向の押し離しを行なう。これによって摩擦ライ
ニング６５８゜６５９はこれらと摩擦結合されている対
応する円板６２４．６２５に押しつけられる。In the embodiment of the second damping device 6° 14 shown in FIG. It has blind holes 656 and 657. A disc-shaped friction lining 658, 659 is received in each of the blind holes 656, 657. the intermediate wall 660 between the two blind holes 658, 657 of the flange 629 has a recess 661 through which a connecting member in the form of a rivet 662 passes; This coupling member includes axially opposed friction linings 658.
, 659 are connected in the axial direction. A tensioned disc spring 663 is provided between the friction lining 658 and the intermediate wall 660 in the axial direction. This disc spring 663 causes the two friction linings 658 and 659 to be axially widened or pushed apart. As a result, the friction linings 658, 659 are pressed against the corresponding discs 624, 625 with which they are frictionally connected.

結合リベット６６２は第１１図に示された組込位置から
両方の摩擦ライニング６５８，６５９を限られた範囲で
軸方向に移動させることを可能にする。両方の摩擦ライ
ニング６５８．６５−９の軸方向の限られた移動は一方
では摩擦ライニング６５８．６５９の摩耗補償を行ない
、他方では第２の減衰装置６１４がまだ取付けられてい
ない状態で摩擦ライニング６５８．６５９と皿ばね６６
３がフランジ６２９に軸方向に固定され、これによって
第２の減衰装置６１４の取付けが著しく簡易化される。The coupling rivet 662 allows a limited axial movement of both friction linings 658, 659 from the installed position shown in FIG. The limited axial movement of both friction linings 658.65-9 on the one hand provides wear compensation of the friction linings 658.659 and on the other hand the friction linings 658 with the second damping device 614 not yet installed. .659 and disc spring 66
3 is axially fixed to the flange 629, which greatly simplifies the installation of the second damping device 614.

第２の減衰装置６１４を組立てる場合には両方の摩擦ラ
イニング６５８と６５９は皿ばね６６３のばね力に抗し
て両方の円板６２４，６２５の間で軸方向に緊定される
。When assembling the second damping device 614, the two friction linings 658 and 659 are tensioned axially between the two disks 624, 625 against the spring force of the disk spring 663.

さらに第１１図から判るように摩擦ライニング６５９は
中間壁６６Ｃ）に直接的に軸方向に支えられている。こ
れに対して摩擦ライニング６５８と中間壁６６０との間
には軸方向の空間が存在している。従って摩擦ライニン
グ６５８は皿ばね６６３の作用に抗して軸方向に袋孔６
５６内で移動させられる。Furthermore, as can be seen in FIG. 11, the friction lining 659 rests directly in the axial direction on the intermediate wall 66C). In contrast, an axial space exists between the friction lining 658 and the intermediate wall 660. Therefore, the friction lining 658 moves axially toward the blind hole 6 against the action of the disc spring 663.
56.

[Brief explanation of the drawing]

図面は本発明の複数の実施例を示すものであって、第１
図は本発明の装置の断面図、第２図は第１図に示された
装置を矢印■の方向から見た部分図、第３図は本発明の
装置の第２の減衰装置の１実施例の断面図、第４図は本
発明の装置の第２の減衰装置の別の１実施例を示した図
。第５図は第４図の■−■線に沿った断面図、第６図は本
発明の装置の第２の減衰装置のさらに別の実施例を示し
た図、第７図と第８図と第９図と第１０図は本発明の装
置の第２の減衰装置の別の実施例を示したもので第８図
は第２−の減衰装置の円板グループの円板を組立られて
いない状態で示した図、第９図は第１０図のＩＸ−ＩＸ
線に沿った断面図、第１１図は本発明の装置の第２の減
衰装置の変化実施例を示した図である。１・・・回転衝撃を吸収する装置、２・・・はずみ車。３．４・・・はずみ質量体、５・・・クランク軸。６・・・固定ねじ、７・・・摩擦クラッチ、８・・・圧
力板。９・・・クラッチ板、１０・・・入力軸、１１・・・ク
ラッチカバー、１２・・・皿ばね、１３・・・第、１の
減衰袋。置、１４・・・第２の減衰装置、１５・・・軸受、１６
・・・アンギュラ形ころがり軸受、１７・・・内レース
。１８・・・孔、１９・・・ピン、２０・・・皿ばね、２
１・・・確保円板、２２・・・付加部、２３・・・室、
２４．２５・・・円板、２６・・・リベット、２７・・
・切欠き、２８・・・張出し部、２９・・・フランジ、
３０・・・皿ばね。３１・・・肩、３２・・・ライニングセグメント、３３
゜３４・・・切欠き、３５・・・蓄力器、３６・・・遊
び、３７．３８・・・円板、３９・・・スペーサピン、
４０・・・蓄力器、４１・・・蓄力器、４２・・・圧力
力ング、４３・・・摩擦リング、４４・・・切欠き、」
５・・・歯。The drawings show several embodiments of the invention, the first
2 is a partial view of the device shown in FIG. 1 as seen from the direction of the arrow ■. FIG. 3 is an implementation of the second damping device of the device of the present invention. FIG. 4 is a cross-sectional view showing another embodiment of the second damping device of the device according to the invention. 5 is a sectional view taken along the line ■-■ in FIG. 4, FIG. 6 is a diagram showing still another embodiment of the second damping device of the device of the present invention, and FIGS. 7 and 8 9 and 10 show another embodiment of the second damping device of the device of the present invention, and FIG. 8 shows the assembled disks of the second damping device group. Figure 9 shows IX-IX in Figure 10.
11 shows a variant embodiment of the second damping device of the device according to the invention; FIG. 1... Device that absorbs rotational shock, 2... Flywheel. 3.4... Spring mass body, 5... Crankshaft. 6...Fixing screw, 7...Friction clutch, 8...Pressure plate. 9... Clutch plate, 10... Input shaft, 11... Clutch cover, 12... Belleville spring, 13... First damping bag. position, 14... second damping device, 15... bearing, 16
...Angular type rolling bearing, 17...Inner race. 18...hole, 19...pin, 20...disc spring, 2
1...Securing disk, 22...Additional part, 23...Chamber,
24.25... Disk, 26... Rivet, 27...
・Notch, 28... overhang, 29... flange,
30... Disc spring. 31... Shoulder, 32... Lining segment, 33
゜34...Notch, 35...Power accumulator, 36...Play, 37.38...Disc, 39...Spacer pin,
40... Energy storage device, 41... Energy storage device, 42... Pressure ring, 43... Friction ring, 44... Notch."
5...Teeth.

Claims

[Claims] 1. A device for absorbing rotational shocks of an internal combustion engine, comprising at least two mutually coaxially arranged damping devices that can rotate relative to each other in a limited manner against the action of damping devices. one of these spring masses can be connected to the internal combustion engine and the other spring mass can be connected to the input of the transmission, and the damping device has an effective force storage in the circumferential direction. and/or friction or sliding elements, in which, in addition to this damping device, at least one second damping device is provided in the torque transmission path between the spring masses. , first damping device (13, 113)
and the second damping device (14, 114, 214, 314, 4
14, 514, 614), respectively, at least two axially spaced discs (37+38, 13
7+138; 24+25, 124+125, 224+2
25, 424+425, 524+525, 624+62
5), each group of disks has a spring mass of the other (3
, 4; 103, 104; 203, 303; 403, 50
3) a common intermediate flange (29, 129, 229, 32
9, 429, 529, 629) are the first and second damping devices (14, 114, 214, 314, 414, 514, 6
14) A rotational impact damping device for an internal combustion engine, characterized in that the device is provided for transmitting rotational moment between. 2. Intermediate flange (29, 129, 229, 329, 4
29, 529, 629) in the radial direction for both disc groups (37+38, 137+138; 24+25, 124
+125, 224+225, 524+525, 624+
625), the damping device according to claim 1. 3. One disk group (37+38, 137+138
) is approximately radial and other disk groups (24+25, 1
24+125, 224+225, 424+425, 52
4+525, 624+625), and the flange (29, 129, 229, 329, 429,
529, 629) for both disc groups (37+38,
137+138; 24+25, 124+125, 224
+225, 424+425, 524+525, 624+
625) in the radial direction.
The device according to paragraph 2 or paragraph 2. 4. Second damping device (14, 114, 214, 314,
414, 514, 614) connected to the first bouncing mass (3, 103)
5, 124+125, 224+225, 424+425
, 524+525, 624+625), the output part of which also constitutes the input part of the first damping device (13, 113) (29, 129, 229, 329,
429, 529, 629) and the output of the first damping device is constituted by both discs (37, 38; 137, 138) connected to the second bouncing mass; Apparatus according to any one of claims 1 to 3. 5, intermediate flange (29, 129, 229, 329, 4
29, 529, 629) and the radially inner disk group (37+38, 137+138) and/or the intermediate flange (29, 129, 229, 329, 429, 5
29, 629) and the radially outer disk group (24+
25, 124+125, 224+225, 424+42
5, 524+525, 624+625). 6. Disc group (13, 113) of the first damping device (13, 113)
37+38; 137+138) is the second bouncy mass (
4, 104) and non-rotatable, and the second damping device (1
4, 114, 214, 314, 414, 514, 614
) disk group (24, 25; 124, 125; 22
4, 225; 424, 425; 524, 525; 624
, 625) is the first bouncy mass (3, 103, 203
, 303, 403, 503) and is non-rotatable. 7. A patent in which the disc group of the first damping device is non-rotatable with respect to the first bouncing mass, and the disc group of the second damping device is non-pivotable with the second bouncing mass. Apparatus according to claims 1 to 3 or 5. 8, Flange (29, 129, 229, 329, 429
, 529, 629) is the second damping device (14, 114,
214, 314, 414, 514, 614) disc groups (24, 25; 124, 125; 224, 225;
424, 425; 524, 525; 624, 625). 9. At least the second damping device (14, 114, 214
, 314, 414, 514, 614) disks (24, 2
5; 124, 125; 224, 225; 424, 425
; 524, 525; 624, 625) and a flange (29, 129, 229, 329, 429, 529, 6
29) between the friction lining or sliding lining (3
2, 132, 249, 432, 532, 658, 656
).) The force device according to claim 8, wherein: 10, one disk (of the second damping device (14, 114)
25, 125) is bouncing in the axial direction and the mass body (3, 4; 10
3, 104), and the other disc (2
4, 124) is movable in the axial direction with respect to the disk (25, 125).
Apparatus according to any one of the preceding paragraphs. 11. Device according to claim 10, in which the axially fixed disc (25, 126) prevents rotation of the other disc (24, 124). 12, a second damping device (14, 1
One of the discs (24, 25, 124, 125) of 14) has an axial protrusion (24a; 126a), and this protrusion (
12. Device according to claim 10, characterized in that 24a; 125a) engages in a recess (27, 127) of the other disc (25, 124). 13. The projections (24a, 25a) are formed by axially extending tongues (24a, 126a) integrally molded on at least one of the discs (24, 25, 124, 125), and the tongues 13. The device according to claim 12, wherein the portion (24a, 125a) projects axially into a cutout (27, 127) provided in the outer periphery of the other disc. 14, the disk (25) fixed in the axial direction has a protrusion (125
Claim 12 or 1 retaining a)
The device according to item 3. 15, an axially movable disk (25) has a protrusion (25a
), the device according to claim 12 or claim 13. 16, the axial projections (24a, 125a) are connected to the discs (24, 25, 124, 1) of the second damping device (14, 114).
25) The device according to any one of claims 12 to 15, wherein the device is provided on the radially outer periphery of at least one of the parts 25). 17, second damping device disc (24, 25, 124, 1
25, 424, 425) (25, 12
5, 424, 425) and the mass body (3, 4, 103
, 104, 403) by means of rivets (26, 126, 455). equipment. 18, second damping device (14, 114, 214, 514
) movable in the axial direction of the disc (24, 125, 225,
524, 526) are power accumulators (30, 130, 232, 5
30) in the axial direction by the other disk (25, 124, 22
18. A device according to any one of claims 9 to 17, wherein the device is loaded towards a device (4, 525, 524). 19. The force accumulator (30, 130) that loads the axially movable disc (24, 124) is activated by the mass body (3, 10)
3), on which an axially immobile disk (25, 125) is fixed; The device described. 20. The device according to claim 19, wherein the energy accumulator (30, 130) is constituted by a disc spring-like member. 21, a disc spring-like member (30, 130) has a slit or is open on the outer periphery, and this member (
The outer circumference of the member (30, 130) is the shoulder (31, 131) of the spring mass (3, 103) supporting this member (30, 130).
).) Apparatus according to claim 20. 22, the axial protrusion (24a) is connected to the flange (29, 12
9) The device according to any one of claims 12 to 21, passing through the cutout of 9). 23. A patent claim in which, when viewed in the circumferential direction, there is play between the notch and the protrusion (24a, 25a) corresponding to the rotation angle allowed for the second damping device (14, 114). The device according to item 22. 24, the individual axial protrusions (24a, 125a)
24. Device according to claim 22 or 23, in which the damping device (14, 114) rests against the contour of a cutout in the flange (29, 129) in order to limit the rotation angle of the damping device (14, 114). 25, flange (29, 229, 329, 429, 52
9) has radial overhangs (28, 228, 328) on the outer periphery.
, 428, 528), and this overhang (28, 228
, 328, 428, 528) is the second damping device (14,
214, 314, 414, 514). 214, 314, 414, 514). 26, the bulge (28) is connected to at least one axial projection (24) of the disc (24, 25) of the second damping device (14).
26. A device according to claim 25, abutting a). 27, second damping device (14, 114, 214, 414
, 514) disk groups (24+25, 124+12
Between this disc and the flange (29, 129, 429, 529) a notch (33, 34; 533, 534) axially aligned with the flange (29, 129, 429, 529) 35, 435, 535). Apparatus according to any one of claims 1 to 26, wherein the device is arranged for receiving a device (35, 435, 535). 28. Device according to claim 27, characterized in that the force accumulator (35, 435, 535) is active in the end range of the automatic angle of the second damping device. 29. The force accumulator (35, 435, 535) serves as a stop for limiting the rotation angle of the second damping device;
An apparatus according to claim 27 or 28. 30. The device according to any one of claims 27 to 29, wherein the energy accumulator (35, 435, 535) is constituted by a coil spring. 31. The energy storage device is composed of a rubber block.
Any one of claims 27 to 29
Equipment described in Section 1. 32, the energy storage device (35, 435, 535) is connected to the flange (2
9, 429, 529) overhang part (28, 428, 52
8), and is provided between the overhanging portions (28, 428,
585). Apparatus according to any one of claims 27 to 31, loaded with: 33, a friction lining effective between the flange (28) and at least one of the discs (24, 25) of the second damping device (14) is fixed to the overhang (28) of the flange (29); Claims 1 to 32 consist of individual segments of friction or sliding material.
Apparatus according to any one of the preceding paragraphs. 34, the flange (29, 229, 329) is concentrically guided through the at least one spring mass;
Apparatus according to any one of claims 1 to 33. 35, at least one of the momentum masses (3, 103, 2
03, 303, 503) of the other spring mass (4, 1
A ring-shaped additional portion (2) extending axially toward (04)
2, 122, 222, 322), and a second damping device (14, 114, 214,
314, 514, 614) and the first damping device (13, 1
13). The device according to any one of claims 1 to 34, wherein: 36, the additional part (22, 122, 222, 322) is the second
damping device (14, 114, 214, 314, 514,
614) is gripped in the axial direction, Claim 31
Apparatus described in section. 37. A groove ( 13
37. A device according to any one of claims 1 to 36, wherein the device is axially and radially supported within 1). 38. A disk (25) fixed in the axial direction of the second damping device (14) is fixed on the end face (22a) of the appendage (22), and the spring mass having the appendage (22) body(
A ring-shaped chamber (23) is formed between the additional part (22) of 3) and the disk (25), and the flange (28) protrudes into this chamber (23) in the radial direction. 37. Device according to claim 35, characterized in that the axially movable disk (24) of the second damping device (14) is received in the chamber (23). 39, first spring mass (3, 103, 203, 30
3, 503) is the additional part (22, 122, 222, 322)
). Apparatus according to any one of claims 35 to 38. 40, disc spring-like member (30) of the second damping device (14)
) is connected to the first bouncing mass (3) and the second damping device (14).
) is tightened between the axially movable disc,
Apparatus according to any one of claims 1 to 39. 41, flange overhangs (28, 228, 328) for concentrically guiding the flanges (29, 229, 329)
) is radially supported on an axial extension (22, 222, 322) of one of the spring masses (3, 203, 303). or a device according to one of the paragraphs. 42. Claim in which a friction or sliding lining (248, 349a) is provided between the extension (222, 322) and the overhang (28, 228) of the flange (29, 229), viewed in the radial direction The device according to item 37. 43, at least the individual overhangs (228) of the flange (229) are each gripped by a cap (249) of friction and/or sliding material, which cap (249) on the one hand has a radius of the flange (229); Claim 41, which is tightened to ensure directional guidance and on the other hand to create a frictional moment between the discs (224, 225) between the second damping device (214).
43. The damping device according to item 42. 44. The cap (249) - viewed in the circumferential direction - has an elastically deformable stop region (253, 254) in the end region.
This stopper range (2
44. The device according to claim 43, wherein the second damping device (214) cooperates with a stop (255) to limit the rotation angle of the second damping device (214). 45, individual overhangs (328) of at least flange (329) for centering flange (329);
) is - viewed in the circumferential direction - a U-shaped guide shoe (349) which bears on the extension (322) of the spring mass (303).
45. A device according to any one of claims 1 to 44, wherein the device is gripped by. 46, side legs (353,
46. Device according to claim 45, in which the second damping device (314) cooperates with a stop (355) which limits the rotational play of the second damping device (314). 47, side legs (353,
47. Device according to claim 45 or 46, characterized in that there is a play (X) between the bulge (354) and the overhang (328), viewed in the circumferential direction. 48, side legs (353,
A power accumulator (357) is located between the
) are provided in claims 45 to 4.
Apparatus according to any one of clauses up to clause 7. 49. Device according to claim 48, characterized in that the force accumulator (357) is made of an elastic material, for example rubber. 50, a first damping device (13, 113) between the flange (29, 129) and the second spring mass (4, 104);
) Stopper (39, 139) that limits circumferential movement of
50. A device according to any one of claims 1 to 49, wherein the device is provided with: 51, the stopper is formed by a spacer pin (39, 139), and this spacer pin (39, 139)
are the discs (37, 38) of the first damping device (13, 113).
; 137, 138) to each other and to the second bouncing mass (4, 104), the flanges (29, 21
51. Device according to claim 50, characterized in that it extends axially through the notch (44) of 9). 52, the spacer pin (39, 139) is attached to the flange (29
52. The device according to claim 51, wherein the rotation angle of the first damping device (13, 113) is limited by abutting the end region of the recess (44) of the first damping device (13, 113). 53, the flange (29) has radial teeth (45) on the inner circumference
53. Device according to any one of claims 50 to 52, characterized in that the teeth (45) engage between the spacer pins (39). 54. Device according to claim 53, characterized in that the teeth (45) are formed by providing a recess (44) in the radially inner region of the flange (29). 55, flange (29, 129, 229, 329, 42
9, 529, 629) is connected to the second bouncy mass (4, 10
55. The device according to claim 1, wherein the device is rotatable in a limited manner relative to 4). 56, discs (424, 42 of the second damping device (414)
5) are axially fixed to each other via a spacer member (455), for example a spacer pin, and at least one of the discs (424, 425) (425) is fixed to the spacer member (455), for example, through a spacer pin.
455) with elastically biased undulations (425a) extending circumferentially between the undulations (425a);
) presses the flange (429) towards the other disk (424). 57, the spacer pin (455) is connected to the disk (424, 425
57. A device according to claim 56, wherein the device is used for securing a device (1) to one of the floating masses. 58, the flange (529) of the second damping device (514)
) are tensioned against the flange (529) by means of circumferentially distributed U-shaped springs (530) or clamps. 57. The apparatus according to any one of the following clauses. 59, a U-shaped spring (530) or clamp axially grips the flange (529) and both discs (524, 525) of the second damping device (514), and the radially extending legs ( 530a, 530b) and the disk (524,
525) from behind in the axial direction, and the flange (
529)
The device according to item 8. 60, one of the spring masses (503) has an axial protrusion (
Notches (555a, 555b) of the discs (524, 525) having a projection (555) that protects the side surface of the flange (529) of the second damping device (514)
engages with and prevents rotation of the discs (524, 525);
Apparatus according to any one of claims 1 to 59. 61, an overhang (5) integrally formed on the outer periphery of the flange (529) between the protrusions (555) in the axial direction when viewed in the circumferential direction;
28) are radially engaged, and the energy storage device (535) is received in the cutout (533, 534) of the disc (524, 525) of the second damping device (514), The force device has a flange (
61. The device according to claim 60, wherein the device is used as an end stop for an overhang (528) of a flange (529). 62, the notch (534) for receiving the energy storage device (535) of one disc (525) is connected to the notch (534) of the other disc (524).
A notch (5) facing the notch (534) in the axial direction
33), the notches (533, 5
The energy accumulator (535) received in the disk (524,
525) in the notch (555a) of the disc (524, 525).
, 555b), the device being offset in the circumferential direction so as to be tightened in the circumferential direction with respect to the protrusion (555) passing through the protrusion (555). 63. Claims 60 to 63, wherein the axial projection is formed by a bolt (555) or a pin, which bolt (555) or pin is fixed to one of the spring masses (503). Apparatus according to any one of clauses up to clause 62. 64, the flange (629) is the second damping device (614)
An axial notch (6
56, 657), and friction blocks (658, 659) are received in these recesses, which friction blocks (658, 659) are connected to the discs (624, 625) of the second damping device (614). 64. A device according to any one of the claims 1 to 63, wherein the device is tightened between .). 65. Claims in which the notches (656, 657) extend through in the axial direction, through which a friction block (658) having a thickness greater than the thickness of the flange is inserted. Apparatus according to paragraph 64. 66. Claims 64 or 6, wherein the friction block (658) is axially movable in the recess (656) and guided radially and/or circumferentially.
The device according to item 5. 67, a pair of friction blocks (658, 659) arranged one after the other is received in the axial recesses (656, 657), between which a force accumulator, for example a disk spring ( 663) is provided, the force store tensioning the friction block (658, 659) towards the disc (624, 625) of the second damping device (614). Apparatus according to any one of paragraphs 66 to 66. 68, the friction blocks (658, 659) and the force accumulator (663) interposed therebetween are the coupling member (662)
are brought together in the axial direction via a connecting member (66
68. Device according to claim 67, wherein 2) allows both friction blocks (658, 659) to move axially to a limited extent against the action of the force accumulator (663). 69, a blind hole (with flanges (629) facing each other in the axial direction)
656, 657), friction blocks (658, 659)
two blind holes (656, 657) having flanges (629) facing each other in the axial direction;
In the intermediate wall (660) between, there is a coupling pin (661) which connects the axially opposed friction blocks (658, 659) through this cutout (661).
662) passes through the friction block, and a force accumulator, for example a disc spring (663), is disposed between at least one of the friction blocks (658, 659) and the intermediate wall (660), and this force accumulator is the friction block. (658, 659) are tightened between the discs (624, 625) of the second damping device (614), and the friction blocks (658, 659) with the coupling members (662) facing each other store force. 64 and 66 to 68, making it possible to carry out a limited movement in the axial direction against the action of the device (663). Device. 70, the first damping device (13, 113) is connected to the second damping device (14, 114, 214, 314, 414, 514,
614), the device according to any one of claims 1 to 69.