JPH0758107B2 - Damper disc spring support structure - Google Patents
Damper disc spring support structureInfo
- Publication number
- JPH0758107B2 JPH0758107B2 JP60257164A JP25716485A JPH0758107B2 JP H0758107 B2 JPH0758107 B2 JP H0758107B2 JP 60257164 A JP60257164 A JP 60257164A JP 25716485 A JP25716485 A JP 25716485A JP H0758107 B2 JPH0758107 B2 JP H0758107B2
- Authority
- JP
- Japan
- Prior art keywords
- flange
- circumferential direction
- sub
- spring
- plates
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
- F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
- F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
-
- 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
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)
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明は摩擦クラッチのクラッチディスク等として使用
されるダンパーディスクに関する。The present invention relates to a damper disc used as a clutch disc of a friction clutch and the like.
（従来の技術） 従来、ダンパーディスクには、出力部であるハブのフラ
ンジと入力部であるサイドプレートとを３種類（第１、
第２、第３）のトーションスプリングで円周方向に連結
した構造のものがある。非捩り状態、すなわちサイドプ
レートがフランジに対して捩れていない状態において、
上記第１スプリングはフランジとサイドプレートの窓孔
の縁に係合しており、第２及び第３のスプリングは、フ
ランジ及びサイドプレートの一方の窓孔の縁だけに係合
している。このように構成されたディスクでは、捩り行
程全体を通して、第１スプリングが圧縮され、捩り角度
が第１の所定値を越えると、第２スプリングが圧縮さ
れ、捩り角度が更に大きい第２の所定値を越えると第３
スプリングが圧縮される。従って捩り特性が３段階に変
化し、優れたトルク振動吸収効果を期待できる。(Prior Art) Conventionally, a damper disk has three types of flanges of a hub which is an output part and side plates which are an input part (first,
There is a structure in which second and third) torsion springs are connected in the circumferential direction. In the non-twisted state, that is, the side plate is not twisted with respect to the flange,
The first spring engages the flange and the edge of the window hole of the side plate, and the second and third springs engage only the edge of the window hole of the flange and the side plate. In the disk configured as described above, the first spring is compressed during the entire twisting stroke, and when the twisting angle exceeds the first predetermined value, the second spring is compressed and the second predetermined value having a larger twisting angle is obtained. Crossing the third
The spring is compressed. Therefore, the torsional characteristics change in three stages, and an excellent torque vibration absorption effect can be expected.
（発明が解決しようとする問題点） ところが、従来構造によると、非捩り状態において、第
２及び第３のスプリングは、いずれもフランジあるいは
サイドプレートの窓孔の縁だけに係合しており、他方の
部材（サイドプレート又はフランジ）の窓孔に対して円
周方向に隙間を隔てている。(Problems to be Solved by the Invention) However, according to the conventional structure, in the non-twisted state, the second and third springs are engaged with only the edge of the window hole of the flange or the side plate, A gap is formed in the circumferential direction with respect to the window hole of the other member (side plate or flange).
従って、仮に非捩り状態において、フランジの窓孔の縁
で第２、第３のスプリングを支持するようにした場合に
は、サイドプレートの窓孔を円周方向に長く形成し、そ
の縁が非捩り状態において第２及び第３のスプリングに
係合しないように構成する必要がある。このように複数
の長い窓孔をサイドプレートに形成する必要があるの
で、隣接する窓孔の間の距離ならびに窓孔とストップピ
ン取付部の間の距離が短くなり、サイドプレートの強度
が低下する。換言すれば、サイドプレートに所定の強度
を与えようとすると、窓孔の長さを充分に長くすること
ができず、そのために捩り角度を充分に大きくして所望
のトルク振動吸収効果を得ることが難しいという問題が
ある。Therefore, if the second and third springs are supported by the edge of the window hole of the flange in the non-twisted state, the window hole of the side plate is formed to be long in the circumferential direction and the edge is It must be configured so as not to engage the second and third springs in the twisted state. Since it is necessary to form a plurality of long window holes in the side plate in this way, the distance between the adjacent window holes and the distance between the window hole and the stop pin mounting portion are shortened, and the strength of the side plate is reduced. . In other words, if the side plate is given a certain strength, the length of the window hole cannot be made sufficiently long. Therefore, the twist angle can be made sufficiently large to obtain the desired torque vibration absorption effect. There is a problem that it is difficult.
又仮に非捩り状態において、サイドプレートの窓孔の縁
で第２、第３のスプリングを支持するようにした場合に
は、フランジの窓孔を円周方向に長く形成し、その縁が
第２及び第３のスプリングに係合しないように構成する
必要がある。従ってこの場合にも、隣接する窓孔の間の
距離が短くなるとともに、窓孔とストップピン挿通用切
欠きの間の距離が短くなり、フランジの強度が低下す
る。換言すれば、フランジの強度上の理由から、捩り角
度を充分に大きくして所望のトルク振動吸収効果を得る
ことが難しいという問題がある。If the edge of the window hole of the side plate supports the second and third springs in the non-twisted state, the window window of the flange is formed to be long in the circumferential direction and the edge is formed into the second edge. And the third spring should not be engaged. Therefore, also in this case, the distance between the adjacent window holes becomes short, and the distance between the window hole and the stop pin insertion notch becomes short, so that the strength of the flange is lowered. In other words, due to the strength of the flange, it is difficult to obtain a desired torque vibration absorption effect by sufficiently increasing the twist angle.
（問題点を解決するための手段） 本発明は、厚板円板状のフランジ３を一体に有する出力
側のハブ２と、フランジ３の両側の回動自在に配置され
内周部が摩擦係数小の摩擦材10を介してフランジ３に圧
接する１対のサブプレート８と、両サブプレート８の外
周部を一体的に連結しフランジ３の円周方向に延びる第
１切欠き18を第１捩り角よりも多少大きい角度に対応す
る隙間Ｑ、ｑを隔てて貫通するサブピン17と、両サブプ
レート８の反フランジ３側に回動自在に配置され内周部
が摩擦係数大の摩擦材11を介してサブプレート８に圧接
する１対の入力側のサイドプレート５と、両サブプレー
ト８の半径方向外側で両サイドプレート５の外周部を一
体的に連結し第１切欠き18の半径方向外側のフランジ３
の円周方向に延びる第２切欠き16を最大捩り角に対応す
る隙間Ｓ、ｓを隔てて貫通するストップピン15と、フラ
ンジ３の内周近傍かつ第１切欠き18の半径方向内側の円
周方向に延びる第１窓孔25内に第１窓孔25に当接する円
周方向両端のばね受け23と共に配置される小弾力の第１
トーションスプリング20と、両ばね受け23より軸方向両
側へ突出して両サブプレート８の円周方向に延びる第２
窓孔26の円周方向両端に当接する突起24と、隣接した第
２切欠き16、16間の一側で両サイドプレート５の円周方
向に延びる第３窓孔30の円周方向両端に当接しフランジ
３の円周方向に延びる第４窓孔29に第１捩り角に対応す
る隙間Ｍ、ｍを隔てて配置される第２トーションスプリ
ング21と、隣接した第２切欠き16、16間の他側でフラン
ジ３の円周方向に延びる第５窓孔27の円周方向両端に当
接し両サイドプレート５の軸方向反フランジ３側へ蒲鉾
状に張出した窪み28の円周方向両端壁31に第２捩り角に
対応する隙間Ｎ、ｎを隔てて配置される第３トーション
スプリング22から成るダンパーディスクのスプリング支
持構造である。(Means for Solving the Problems) In the present invention, a hub 2 on the output side integrally having a thick disk-shaped flange 3 and rotatably arranged inner peripheral portions on both sides of the flange 3 have a friction coefficient. A pair of sub-plates 8 pressed against the flange 3 via a small friction material 10 and a first notch 18 that integrally connects the outer peripheral portions of both the sub-plates 8 and extends in the circumferential direction of the flange 3 are provided. A sub pin 17 penetrating through gaps Q and q corresponding to an angle slightly larger than the torsion angle, and a friction material 11 having a large friction coefficient on the inner peripheral portion, which is rotatably arranged on the side opposite to the flange 3 of both sub plates 8. The pair of input side plates 5 that are pressed against the sub-plates 8 via the outer circumferences of the side plates 5 on the outer sides of the sub-plates 8 in the radial direction. Outer flange 3
Of the stop pin 15 penetrating the second notch 16 extending in the circumferential direction with the gaps S and s corresponding to the maximum torsion angle, and the circle near the inner circumference of the flange 3 and radially inward of the first notch 18. The first small elastic force is arranged in the first window hole 25 extending in the circumferential direction together with the spring bearings 23 at both ends in the circumferential direction that abut the first window hole 25.
The torsion spring 20 and a second spring receiver 23 that projects axially on both sides and extends in the circumferential direction of both sub-plates 8.
The projections 24 that abut on both ends of the window hole 26 in the circumferential direction and the ends of the third window hole 30 that extend in the circumferential direction of both the side plates 5 on one side between the adjacent second notches 16 and 16 are provided at both ends in the circumferential direction. Between the second torsion spring 21 arranged in contact with the fourth window hole 29 extending in the circumferential direction of the flange 3 with a gap M, m corresponding to the first torsion angle, and the adjacent second notches 16, 16. On both sides of the fifth window hole 27 extending in the circumferential direction of the flange 3 on the other side, the both ends of the circumferential direction both ends of the recess 28 that abuts on both ends in the circumferential direction of the fifth window hole 27 and protrudes in the shape of a semi-cylindrical shaft toward the flange 3 side opposite to the axial direction of both side plates 5. 31 is a spring support structure for a damper disk, which is composed of a third torsion spring 22 which is arranged with a gap N corresponding to the second torsion angle, n.
（作用） 上記構成によると、入力部（サイドプレート５、サブプ
レート８）から出力部（ハブ２）にトルクを伝達する場
合、第１〜第３のトーションスプリング20、21、22が圧
縮され、入力部が出力部に対して捩れる。(Operation) According to the above configuration, when torque is transmitted from the input section (side plate 5, sub-plate 8) to the output section (hub 2), the first to third torsion springs 20, 21, 22 are compressed, The input section is twisted with respect to the output section.
そして捩り角度が第１の所定値（第１捩り角用隙間Ｍ、
ｍ）よりも小さい間は、第１トーションスプリング20だ
けが圧縮される。従って僅かなトルク変動に対して捩り
角度は大きく変化する。The twist angle is a first predetermined value (the first twist angle gap M,
Only the first torsion spring 20 is compressed while it is smaller than m). Therefore, the torsion angle greatly changes with a slight torque fluctuation.
捩り角度が第１の所定値を越えると、それまで入力部の
係合部（第３窓孔30）だけで支持されていた第２トーシ
ョンスプリング21が出力部の係合部（第４窓孔29）にも
係合し、第２トーションスプリング21が圧縮され始め
る。従ってトルク変動に対する捩り角度の変化率は小さ
くなる。When the twist angle exceeds the first predetermined value, the second torsion spring 21, which has been supported only by the engaging portion of the input portion (third window hole 30) until then, becomes the engaging portion of the output portion (fourth window hole). 29), and the second torsion spring 21 starts to be compressed. Therefore, the rate of change of the torsion angle with respect to the torque fluctuation becomes small.
捩り角度が第２の所定値（第２捩り角用隙間Ｎ、ｎ）を
越えると、それまで出力部の係合部（第５窓孔27）だけ
で支持されていた第３トーションスプリング22が入力部
の係合部（窪み28の端壁31）にも係合し、第３トーショ
ンスプリング22が圧縮され始める。従ってトルク変動に
対する捩り角度の変化率は更に小さくなる。When the twist angle exceeds the second predetermined value (the second twist angle gap N, n), the third torsion spring 22 which has been supported only by the engagement portion (fifth window hole 27) of the output portion until then. The engagement portion of the input portion (the end wall 31 of the recess 28) is also engaged, and the third torsion spring 22 starts to be compressed. Therefore, the rate of change of the torsion angle with respect to the torque fluctuation is further reduced.
（実施例） 第１図は本発明実施例のクラッチディスクの一部切欠き
正面図、第２図は第１図のII−II断面図である。第２図
において、出力軸１（中心線のみ図示）にスプライン嵌
合するハブ２は環状のフランジ３を外周に一体に備えて
いる。このハブ２とフランジ３は出力部を構成してい
る。フランジ３の両側には１対の環状サイドプレート５
が配置してある。一方のサイドプレート５の外周部には
クッショニングプレート６を介してフェーシング７が連
結されている。又各サイドプレート５とフランジ３の間
には環状のサブプレート８が介装されている。サイドプ
レート５とサブプレート８は入力部を構成している。(Embodiment) FIG. 1 is a partially cutaway front view of a clutch disc according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along line II-II of FIG. In FIG. 2, the hub 2 that is spline-fitted to the output shaft 1 (only the center line is shown) integrally includes an annular flange 3 on the outer circumference. The hub 2 and the flange 3 form an output section. A pair of annular side plates 5 is provided on both sides of the flange 3.
Has been placed. A facing 7 is connected to an outer peripheral portion of one side plate 5 via a cushioning plate 6. An annular sub-plate 8 is interposed between each side plate 5 and the flange 3. The side plate 5 and the sub plate 8 form an input unit.
各サブプレート８の内周部とフランジ３の間には摩擦係
数の小さい摩擦材10が設けてある。各サブプレート８の
内周部とサイドプレート５の間には摩擦係数の大きい摩
擦材11が介装されている。摩擦材10、11は、例えばフリ
クションプレート、フリクションワッシャ、ウエーブス
プリングで構成されている。ハブ２の第２図で左半部の
外周面には筒状スリーブ12が嵌合しており、スリーブ12
の外周面にサイドプレート５やサブプレート８、摩擦材
10、11の内周が嵌合している。A friction material 10 having a small friction coefficient is provided between the inner peripheral portion of each sub-plate 8 and the flange 3. A friction material 11 having a large friction coefficient is interposed between the inner peripheral portion of each sub plate 8 and the side plate 5. The friction materials 10 and 11 are composed of, for example, friction plates, friction washers, and wave springs. A tubular sleeve 12 is fitted on the outer peripheral surface of the left half of the hub 2 in FIG.
Side plate 5, sub-plate 8, friction material on the outer peripheral surface of
The inner circumferences of 10 and 11 are fitted together.
両サイドプレート５は軸方向（出力軸１と平行な方向）
のストップピン15により外周部が連結されており、フラ
ンジ３の外周部にはストップピン15を通すための第２切
欠き16が設けてある。両サブプレート８も軸方向のサブ
ピン17により外周部が連結されており、フランジ３には
サブピン17を通すための第１切欠き18が設けてある。Both side plates 5 are in the axial direction (direction parallel to the output shaft 1)
The outer peripheral portions of the flanges 3 are connected to each other by the stop pins 15, and a second notch 16 is formed on the outer peripheral portion of the flange 3 for allowing the stop pins 15 to pass therethrough. Both sub-plates 8 are also connected at their outer peripheral portions by axial sub-pins 17, and the flange 3 is provided with a first notch 18 through which the sub-pins 17 pass.
両サイドプレート５の内周側部分の間には第１トーショ
ンスプリング20（圧縮コイルスプリング）が設けてあ
る。スプリング20はフランジ３に設けた第１窓孔25内に
位置しており、両端がばね受け23に着座している。ばね
受け23は軸方向両側へ突出した突起24を備えており、突
起24がサブプレート８の第２窓孔26に入り込んでいる。A first torsion spring 20 (compression coil spring) is provided between the inner peripheral portions of both side plates 5. The spring 20 is located in the first window hole 25 provided in the flange 3, and both ends of the spring 20 are seated on the spring receiver 23. The spring bearing 23 is provided with a protrusion 24 protruding toward both sides in the axial direction, and the protrusion 24 is inserted into the second window hole 26 of the sub plate 8.
両サイドプレート５の外周側部分の間には第３トーショ
ンスプリング22（圧縮コイルスプリング）が設けてあ
る。スプリング22はフランジ３に設けた第５窓孔27内に
位置しており、両サイドプレート５の内面にはスプリン
グ22が入り込む窪み28が設けてあり、スプリング22の両
端は窪み28の端壁31に対向している。A third torsion spring 22 (compression coil spring) is provided between the outer peripheral portions of both side plates 5. The spring 22 is located in a fifth window hole 27 provided in the flange 3, and a recess 28 into which the spring 22 is inserted is provided on the inner surfaces of both side plates 5, and both ends of the spring 22 are end walls 31 of the recess 28. Is facing.
第１図の如く、これらのスプリング20、22は円周方向に
間隔を隔てて例えば３個ずつ設けてあり、それぞれ円周
方向に延びている。更に図示のデイスクの外周部には、
３個の第２トーションスプリング21が設けてある。各ス
プリング21は同芯に配置した大径及び小径の圧縮コイル
スプリングで構成されており、円周方向に延びる姿勢で
隣接する各２個の第３スプリング22の間に配置されてい
る。フランジ３及びサイドプレート５にはスプリング21
を収容するための第４、第３窓孔29、30が設けてある。As shown in FIG. 1, these springs 20 and 22 are provided at intervals in the circumferential direction, for example, three springs each, and each extends in the circumferential direction. Furthermore, on the outer peripheral part of the illustrated disk,
Three second torsion springs 21 are provided. Each spring 21 is composed of a large-diameter and small-diameter compression coil spring arranged concentrically, and is arranged between two adjacent third springs 22 in a posture extending in the circumferential direction. Spring 21 on flange 3 and side plate 5
Are provided with fourth and third window holes 29 and 30.
第１図に示す非捩り状態において、各部は次のような状
態にある。各スプリング20の両端のばね受け23はフラン
ジ３及びサブプレート８の窓孔25、26の縁に係合してい
る。各スプリング22の両端はフランジ３の窓孔27の縁だ
けに係合しており、サイドプレート５の窪み28の端壁31
に対して第２捩り角（例えば＋16.5度、−7.5度）に相
当する隙間Ｎ、ｎを円周方向に隔てている。各スプリン
グ21の両端はサイドプレート５の窓孔30の縁だけに係合
しており、フランジ３の窓孔29に対して第１捩り角（例
えば＋11度、−５度）に相当する隙間Ｍ、ｍを円周方向
に隔てている。In the non-twisted state shown in FIG. 1, each part is in the following state. Spring supports 23 at both ends of each spring 20 engage with the edges of the window holes 25 and 26 of the flange 3 and the sub-plate 8. Both ends of each spring 22 are engaged only with the edge of the window hole 27 of the flange 3, and the end wall 31 of the recess 28 of the side plate 5 is engaged.
On the other hand, the gaps N and n corresponding to the second torsion angle (for example, +16.5 degrees and -7.5 degrees) are separated in the circumferential direction. Both ends of each spring 21 are engaged only with the edge of the window hole 30 of the side plate 5, and a gap M corresponding to the first twist angle (for example +11 degrees, -5 degrees) with respect to the window hole 29 of the flange 3. , M are circumferentially separated.
更に非捩り状態では、各ストップピン15は切欠き16の縁
に対して最大捩り角（例えば＋18度、−９度）に相当す
る隙間Ｓ、ｓを円周方向に隔てている。各サブピン17は
切欠き18の縁に対して例えば上記第１捩り角よりも多少
大きい角度に相当する隙間Ｑ、ｑを円周方向に隔ててい
る。Further, in the non-twisted state, each stop pin 15 is circumferentially separated from the edge of the notch 16 by a gap S, s corresponding to the maximum twist angle (for example, + 18 °, −9 °). The sub-pins 17 are circumferentially separated from the edge of the notch 18 by gaps Q and q corresponding to, for example, an angle slightly larger than the first twist angle.
次に実施例の装置の作用を説明する。図示されていない
機構によりフェーシング７のフライホイールに押付ける
ことにより、フライホイールからフェーシング７を介し
てサイドプレート５にトルクが伝達される。このトルク
はサイドプレート５からスプリング20、21、22を介して
フランジ３へ伝わり、フランジ３からハブ２を介して出
力軸１へ伝わる。この動作において、スプリング20、2
1、22が伝達トルクに対応する力で圧縮され、サイドプ
レート５やサブプレート８がフランジ３に対して捩れ
る。Next, the operation of the apparatus of the embodiment will be described. By pressing the flywheel of the facing 7 by a mechanism (not shown), torque is transmitted from the flywheel to the side plate 5 via the facing 7. This torque is transmitted from the side plate 5 to the flange 3 via the springs 20, 21, 22 and from the flange 3 to the output shaft 1 via the hub 2. In this movement, the springs 20, 2
1, 22 are compressed by a force corresponding to the transmission torque, and the side plate 5 and the sub plate 8 are twisted with respect to the flange 3.
上記動作において、伝達トルクが小さい間は摩擦材11の
摩擦力によりサイドプレート５とサブプレート８が相対
捩り不能に連結される。従って伝達トルクが小さい間、
すなわち捩り角度が第１の所定値よりも小さい間は、サ
ブプレート８とフランジ３の間においてスプリング20だ
けが圧縮される。従って伝達トルクの僅かな変化に対し
て捩り角は大きく変化する。又この間は摩擦材10の表面
に滑りが生じるので、その滑りに起因する摩擦により、
捩り特性に僅かなヒステリシストルクが生じる。In the above operation, the side plate 5 and the sub-plate 8 are connected so as not to be twisted relative to each other by the frictional force of the friction material 11 while the transmission torque is small. Therefore, while the transmission torque is small,
That is, while the twist angle is smaller than the first predetermined value, only the spring 20 is compressed between the sub plate 8 and the flange 3. Therefore, the torsion angle changes greatly with a slight change in the transmission torque. Also, during this period, slippage occurs on the surface of the friction material 10, and due to the friction caused by the slippage,
A slight hysteresis torque is generated in the torsion characteristic.
捩り角度が第１の所定値を越えると、それまでサイドプ
レート５の窓孔30だけで支持されていたスプリング21が
フランジ３の窓孔29にも係合し、スプリング21が圧縮さ
れ始める。従って伝達トルクの変化に対する捩り角度の
変化率は小さくなる。When the twist angle exceeds the first predetermined value, the spring 21, which was previously supported only by the window hole 30 of the side plate 5, engages with the window hole 29 of the flange 3, and the spring 21 starts to be compressed. Therefore, the rate of change of the torsion angle with respect to the change of the transmission torque becomes small.
捩り角度が第２の所定値を越えると、それまでフランジ
３の窓孔27だけで支持されていたスプリング22がサイド
プレート５の窪み28の端壁31にも係合し、スプリング22
が圧縮され始める。従って伝達トルクの変化に対する捩
り角度の変化率は更に小さくなる。When the twisting angle exceeds the second predetermined value, the spring 22 which was previously supported only by the window hole 27 of the flange 3 also engages with the end wall 31 of the recess 28 of the side plate 5, and the spring 22
Begins to be compressed. Therefore, the rate of change of the torsion angle with respect to the change of the transmission torque becomes smaller.
上記第２及び第３の捩り動作では、サブピン17が第１切
欠き18に係合するので、サブプレート８はフランジ３に
相対捩り不能に連結される。従ってサイドプレート５が
サブプレート８に対して捩れて摩擦材11の表面に滑りが
生じ、その滑りに起因する摩擦により捩り特性に大きい
ヒステリシストルクが生じる。In the second and third twisting operations, the sub-pin 17 engages with the first notch 18, so that the sub-plate 8 is coupled to the flange 3 in a non-twistable manner. Therefore, the side plate 5 is twisted with respect to the sub plate 8 to cause a slip on the surface of the friction material 11, and the friction resulting from the slip causes a large hysteresis torque in the torsion characteristic.
捩り角度が最大値になると、ストップピン15が第２切欠
き16の縁に係合し、それ以上の捩りは阻止される。When the twist angle reaches its maximum value, the stop pin 15 engages with the edge of the second notch 16 and further twist is prevented.
フランジ３には第２切欠き16の半径方向内側に第１切欠
き18があり、第１切欠き18の内側に第１窓孔25があり、
隣接した第２切欠き16、16の間の一側に第４窓孔29を設
け、他側に第５窓孔27を設け、サイドプレート５には第
２トーションスプリング21を支持する第３窓孔30の隣に
第３トーションスプリング22を支持する窓孔は設けず
に、蒲鉾形の窪み28の端壁31を設けている。The flange 3 has a first notch 18 radially inside the second notch 16, and a first window hole 25 inside the first notch 18,
A third window for supporting the second torsion spring 21 in the side plate 5 is provided with a fourth window hole 29 on one side between the adjacent second notches 16, 16 and a fifth window hole 27 on the other side. Next to the hole 30, a window hole for supporting the third torsion spring 22 is not provided, but an end wall 31 of a semi-cylindrical recess 28 is provided.
（発明の効果） 以上説明したように本発明の構造によると、フランジ３
に設けられる第２、第３スプリング21、22用の窓孔29、
27（スプリング係合部）の全長は、非捩り状態における
スプリング21、22の全長に比べ、第１捩り角に相当する
隙間Ｍ、ｍの和だけ長くすればよい。又サイドプレート
５に設けられる第２、第３スプリング21、22用の窓孔30
と窪み28（スプリング係合部）の全長は、非捩り状態に
おけるスプリング21、22の全長に比べ、第２捩り角に相
当する隙間Ｎ、ｎの和だけ長くすればよい。(Effect of the Invention) As described above, according to the structure of the present invention, the flange 3
Window holes 29 for the second and third springs 21 and 22 provided in the
The total length of 27 (spring engaging portion) may be longer than the total length of the springs 21 and 22 in the non-twisted state by the sum of the gaps M and m corresponding to the first torsion angle. Also, window holes 30 for the second and third springs 21 and 22 provided in the side plate 5
The total length of the recess 28 (spring engaging portion) may be set longer than the total length of the springs 21 and 22 in the non-twisted state by the sum of the gaps N and n corresponding to the second torsion angle.
従って、第１捩り角に相当する隙間Ｍ、ｍ及び第２捩り
角に相当する隙間Ｎ、ｎの両方をフランジ３又はサイド
プレート５だけに形成する場合に比べ、フランジ３又は
サイドプレート５の窓孔の全長を短くでき、強度を高め
ることができる。従って上記隙間を長くして最大捩り角
度を大きく設定し、所望のトルク振動吸収効果を得るこ
とができる。Therefore, as compared with the case where both the gaps M and m corresponding to the first twist angle and the gaps N and n corresponding to the second twist angle are formed only in the flange 3 or the side plate 5, the window of the flange 3 or the side plate 5 is formed. The total length of the holes can be shortened and the strength can be increased. Therefore, it is possible to obtain the desired torque vibration absorption effect by lengthening the gap and setting the maximum torsion angle large.
しかも本発明によると、最も荷重の掛かる第２捩り角
（隙間Ｎ、ｎ）以上の捩り角範囲で、サイドプレート５
には窪み28の円周方向両端壁31が第３トーションスプリ
ング22から荷重を受けるようにして強度低下を伴なう窓
孔を無くしたので、サイドプレート５の強度を確保する
ことが可能となる。Moreover, according to the present invention, the side plate 5 is provided in a twist angle range equal to or greater than the second twist angle (gap N, n) at which the load is most applied.
Since both ends 31 in the circumferential direction of the recess 28 receive the load from the third torsion spring 22 and the window hole accompanied by the decrease in strength is eliminated, the strength of the side plate 5 can be secured. .
又フランジ３の第２切欠き16の半径方向内側に順次第１
切欠き18と第１窓孔25を設けたので、第４窓孔29、第５
窓孔27に円周方向に大きくしてもフランジ３の強度の低
下を可及的に防止することができる。In addition, the first notch is formed on the inner side of the second notch 16 of the flange 3 in the radial direction.
Since the notch 18 and the first window hole 25 are provided, the fourth window hole 29 and the fifth window hole
Even if the window hole 27 is enlarged in the circumferential direction, the reduction in the strength of the flange 3 can be prevented as much as possible.
第１図は本発明実施例のクラッチディスクの一部切欠き
正面図、第２図は第１図のII−II断面図である。３……
フランジ（出力部）、５……サイドプレート（入力
部）、20……第１トーションスプリング、21……第２ト
ーションスプリング、22……第３トーションスプリン
グ、25、26、27、29、30……窓孔（スプリング係合
部）、28……窪み（スプリング係合部）。1 is a partially cutaway front view of a clutch disc according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along line II-II of FIG. 3 ...
Flange (output part), 5 ... side plate (input part), 20 ... first torsion spring, 21 ... second torsion spring, 22 ... third torsion spring, 25, 26, 27, 29, 30 ... … Window hole (spring engagement part), 28… Recess (spring engagement part).
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭60−84431（ＪＰ，Ａ) 特開 昭58−196324（ＪＰ，Ａ) 特開 昭59−62725（ＪＰ，Ａ) 特開 昭57−134019（ＪＰ，Ａ) 実開 昭59−142522（ＪＰ，Ｕ) ─────────────────────────────────────────────────── ─── Continuation of front page (56) Reference JP-A-60-84431 (JP, A) JP-A-58-196324 (JP, A) JP-A-59-62725 (JP, A) JP-A-57- 134019 (JP, A) Actual development Sho 59-142522 (JP, U)
Claims (1)
る出力側のハブ（２）と、フランジ（３）の両側の回動
自在に配置され内周部が摩擦係数小の摩擦材（10）を介
してフランジ（３）に圧接する１対のサブプレート
（８）と、両サブプレート（８）の外周部を一体的に連
結しフランジ（３）の円周方向に延びる第１切欠き（1
8）を第１捩り角よりも多少大きい角度に対応する隙間
（Ｑ、ｑ）を隔てて貫通するサブピン（17）と、両サブ
プレート（８）の反フランジ（３）側に回動自在に配置
され内周部が摩擦係数大の摩擦材（11）を介してサブプ
レート（８）に圧接する１対の入力側のサイドプレート
（５）と、両サブプレート（８）の半径方向外側で両サ
イドプレート（５）の外周部を一体的に連結し第１切欠
き（18）の半径方向外側のフランジ（３）の円周方向に
延びる第２切欠き（16）を最大捩り角に対応する隙間
（Ｓ、ｓ）を隔てて貫通するストップピン（15）と、フ
ランジ（３）の内周近傍かつ第１切欠き（18）の半径方
向内側の円周方向に延びる第１窓孔（25）内に第１窓孔
（25）に当接する円周方向両端のばね受け（23）と共に
配置される小弾力の第１トーションスプリング（20）
と、両ばね受け（23）より軸方向両側へ突出して両サブ
プレート（８）の円周方向に延びる第２窓孔（26）の円
周方向両端に当接する突起（24）と、隣接した第２切欠
き（16、16）間の一側で両サイドプレート（５）の円周
方向に延びる第３窓孔（30）の円周方向両端に当接しフ
ランジ（３）の円周方向に延びる第４窓孔（29）に第１
捩り角に対応する隙間（Ｍ、ｍ）を隔てて配置される第
２トーションスプリング（21）と、隣接した第２切欠き
（16、16）間の他側でフランジ（３）の円周方向に延び
る第５窓孔（27）の円周方向両端に当接し両サイドプレ
ート（５）の軸方向反フランジ（３）側へ蒲鉾状に張出
した窪み（28）の円周方向両端壁（31）に第２捩り角に
対応する隙間（Ｎ、ｎ）を隔てて配置される第３トーシ
ョンスプリング（22）から成るダンパーディスクのスプ
リング支持構造。1. A hub (2) on the output side integrally including a thick disk-shaped flange (3), and friction rotatably arranged on both sides of the flange (3) and having an inner peripheral portion having a small friction coefficient. A pair of sub-plates (8) pressed against the flange (3) through the material (10) and the outer peripheral portions of both sub-plates (8) are integrally connected to each other and extend in the circumferential direction of the flange (3). 1 notch (1
8) The sub-pin (17) that penetrates through 8) with a gap (Q, q) corresponding to an angle slightly larger than the first twist angle, and the sub-pin (8) can be pivoted to the opposite flange (3) side. A pair of input-side side plates (5), which are arranged and whose inner periphery is in pressure contact with the sub-plate (8) through a friction material (11) having a large friction coefficient, and on the outer side in the radial direction of both sub-plates (8) The second notch (16) extending in the circumferential direction of the flange (3) radially outside the first notch (18) that integrally connects the outer peripheral portions of both side plates (5) corresponds to the maximum twist angle. The stop pin (15) penetrating through the gap (S, s) and the first window hole (circumferentially extending near the inner circumference of the flange (3) and radially inward of the first notch (18)). The first toe having a small elastic force, which is arranged with the spring bearings (23) at both ends in the circumferential direction, which are in contact with the first window hole (25). Spring (20)
And a protrusion (24) which is projected from both spring bearings (23) axially on both sides and abuts on both circumferential ends of the second window holes (26) extending in the circumferential direction of both sub-plates (8). In the circumferential direction of the flange (3), the third window holes (30) extending in the circumferential direction of both side plates (5) are brought into contact with the circumferential ends of the flange (3) on one side between the second notches (16, 16). First in the extending fourth window (29)
The second torsion spring (21) is arranged with a gap (M, m) corresponding to the torsion angle and the circumferential direction of the flange (3) on the other side between the adjacent second notches (16, 16). End walls (31) of the recesses (28) that are in contact with both ends of the fifth window hole (27) extending in the circumferential direction in the direction of the axially opposite flange (3) of both side plates (5) and are in the shape of a hook. ) Is a spring support structure for a damper disk, which includes a third torsion spring (22) arranged with a gap (N, n) corresponding to the second torsion angle.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60257164A JPH0758107B2 (en) | 1985-11-15 | 1985-11-15 | Damper disc spring support structure |
| GB8626892A GB2183006B (en) | 1985-11-15 | 1986-11-11 | Structure for supporting springs in a damper disc |
| KR1019860009520A KR920008169B1 (en) | 1985-11-15 | 1986-11-12 | Structure for supporting springs in a damper disc |
| FR8615845A FR2591697B1 (en) | 1985-11-15 | 1986-11-14 | DEVICE FOR SUPPORTING SPRINGS IN A SHOCK ABSORBER |
| DE19863638938 DE3638938A1 (en) | 1985-11-15 | 1986-11-14 | HOLDING CONSTRUCTION FOR THE SPRINGS OF A DAMPING DISC |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60257164A JPH0758107B2 (en) | 1985-11-15 | 1985-11-15 | Damper disc spring support structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62118122A JPS62118122A (en) | 1987-05-29 |
| JPH0758107B2 true JPH0758107B2 (en) | 1995-06-21 |
Family
ID=17302584
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60257164A Expired - Lifetime JPH0758107B2 (en) | 1985-11-15 | 1985-11-15 | Damper disc spring support structure |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPH0758107B2 (en) |
| KR (1) | KR920008169B1 (en) |
| DE (1) | DE3638938A1 (en) |
| FR (1) | FR2591697B1 (en) |
| GB (1) | GB2183006B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014516145A (en) * | 2011-06-07 | 2014-07-07 | ヴァレオ アンブラヤージュ | Torsional damper device especially for automobile transmissions |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19536513C2 (en) * | 1994-09-29 | 2002-02-14 | Exedy Corp | Vibration damper for a disc clutch |
| FR2735548B1 (en) * | 1995-06-19 | 1997-08-08 | Valeo | TORSION DAMPING DEVICE |
| JP3732021B2 (en) * | 1998-09-18 | 2006-01-05 | 株式会社エクセディ | Damper mechanism |
| JP2002213535A (en) * | 2001-01-18 | 2002-07-31 | Exedy Corp | Damper mechanism |
| CN105485200A (en) * | 2016-01-15 | 2016-04-13 | 中国重汽集团济南动力有限公司 | Clutch driven disc used for commercial vehicle |
| CN107339333A (en) * | 2016-12-28 | 2017-11-10 | 安徽江淮汽车集团股份有限公司 | A kind of clutch driven plate vibration-proof structure |
| CN112855798B (en) * | 2021-03-03 | 2023-01-03 | 舍弗勒技术股份两合公司 | Torque limiting device, torque transmission device, and vehicle |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2293781A (en) * | 1939-07-22 | 1942-08-25 | Thelander W Vincent | Friction clutch plate |
| FR77424E (en) * | 1960-03-29 | 1962-03-02 | Ferodo Sa | Motor vehicle transmissions improvements |
| FR1525291A (en) * | 1967-04-05 | 1968-05-17 | Ferodo Sa | Improvements to damper hub clutch friction |
| FR2162702A5 (en) * | 1971-11-29 | 1973-07-20 | Ferodo Sa | |
| JPS57134019A (en) * | 1981-02-13 | 1982-08-19 | Daikin Mfg Co Ltd | Clutch disc |
| FR2507720A1 (en) * | 1981-06-16 | 1982-12-17 | Automotive Prod France | FRICTION CLUTCH OUTPUT DISC |
| JPS58196324A (en) * | 1982-05-13 | 1983-11-15 | Aisin Seiki Co Ltd | Clutch disc |
| US4618048A (en) * | 1982-06-29 | 1986-10-21 | Aisin Seiki Kabushiki Kaisha | Clutch disk assembly |
| DE3230663C2 (en) * | 1982-08-18 | 1986-02-27 | Fichtel & Sachs Ag, 8720 Schweinfurt | Clutch disc with torsional vibration damper and control plate |
| JPS5962725A (en) * | 1982-09-30 | 1984-04-10 | Aisin Seiki Co Ltd | Frictional type engaging disc device |
| JPS60112727U (en) * | 1984-01-05 | 1985-07-30 | 株式会社 大金製作所 | damper disc |
| DE3415927A1 (en) * | 1984-04-28 | 1985-10-31 | Fichtel & Sachs Ag, 8720 Schweinfurt | Torsional vibration damper with idle suspension that can be loaded in both directions of rotation |
| JPS6141019A (en) * | 1984-07-31 | 1986-02-27 | Daikin Mfg Co Ltd | Damper disc |
-
1985
- 1985-11-15 JP JP60257164A patent/JPH0758107B2/en not_active Expired - Lifetime
-
1986
- 1986-11-11 GB GB8626892A patent/GB2183006B/en not_active Expired - Lifetime
- 1986-11-12 KR KR1019860009520A patent/KR920008169B1/en not_active IP Right Cessation
- 1986-11-14 DE DE19863638938 patent/DE3638938A1/en not_active Ceased
- 1986-11-14 FR FR8615845A patent/FR2591697B1/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014516145A (en) * | 2011-06-07 | 2014-07-07 | ヴァレオ アンブラヤージュ | Torsional damper device especially for automobile transmissions |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62118122A (en) | 1987-05-29 |
| GB2183006A (en) | 1987-05-28 |
| KR870005194A (en) | 1987-06-05 |
| GB8626892D0 (en) | 1986-12-10 |
| KR920008169B1 (en) | 1992-09-24 |
| FR2591697B1 (en) | 1989-11-17 |
| FR2591697A1 (en) | 1987-06-19 |
| GB2183006B (en) | 1990-09-12 |
| DE3638938A1 (en) | 1987-05-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| EXPY | Cancellation because of completion of term |