JPH0155690B2 - - Google Patents
Info
- Publication number
- JPH0155690B2 JPH0155690B2 JP71482A JP71482A JPH0155690B2 JP H0155690 B2 JPH0155690 B2 JP H0155690B2 JP 71482 A JP71482 A JP 71482A JP 71482 A JP71482 A JP 71482A JP H0155690 B2 JPH0155690 B2 JP H0155690B2
- Authority
- JP
- Japan
- Prior art keywords
- flange
- spring
- hub
- teeth
- sides
- 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
Links
- 230000002093 peripheral effect Effects 0.000 claims description 8
- 239000002783 friction material Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 229910000639 Spring steel Inorganic materials 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/12313—Wound springs characterised by the dimension or shape of spring-containing windows
-
- 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
- F16F15/12373—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 the sets of springs being arranged at substantially the same radius
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Description
【発明の詳細な説明】
本発明は主として自動車用クラツチに適したダ
ンパーデイスク、特に内周面にスプライン内歯を
有し、外周面に略環状板形の内周側フランジを有
する第１ハブと、内周側フランジの外歯に回転方
向の遊びを隔てて嵌合する内歯を有する外周側フ
ランジと、両フランジの両側に配置された回動自
在のサイドプレートと、外周側フランジとサイド
プレートとの間に挿入されたトーシヨンスプリン
グを有するダンパーデイスクに関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION The present invention mainly relates to a damper disk suitable for a clutch for an automobile, and particularly to a first hub having spline internal teeth on the inner circumferential surface and a generally annular plate-shaped inner circumferential flange on the outer circumferential surface. , an outer flange having internal teeth that fit into the external teeth of the inner flange with rotational play, a rotatable side plate disposed on both sides of both flanges, and the outer flange and the side plate. This invention relates to a damper disk having a torsion spring inserted between the damper disk and the torsion spring.
ダンパーデイスクのハブフランジを内周側フラ
ンジと外周側フランジとに分割し、両フランジを
内歯と外歯で円周方向に遊びを隔てて嵌した所謂
分割形ダンパーデイスクにおいては、既に弱い捩
りスプリングをトーシヨンスプリングとして両ハ
ブ間に介装し、低捩り角度範囲の捩り特性を与え
る第１段目のスプリングとしているダンパーデイ
スクが出願されている（特願昭56−20510）。しか
しその構成では、外周側フランジに切欠きや窓孔
を設け、更に第２フランジを挾持するプレートを
設ける必要があり、構造が複雑になるばかりでな
く、スプリングのスペースとハブの動力伝達部の
強度とが干渉し合うため、強度確保上ダンパーデ
イスクの捩り角度としては20度程度が限界であ
る。 In a so-called split damper disk, in which the hub flange of the damper disk is divided into an inner flange and an outer flange, and both flanges are fitted with inner and outer teeth with some play in the circumferential direction, the torsion spring is already weak. A damper disk has been filed (Japanese Patent Application No. 56-20510) in which a torsion spring is interposed between both hubs, and the first stage spring provides torsional characteristics in a low torsion angle range. However, with this configuration, it is necessary to provide a notch or window hole in the outer flange, and also to provide a plate to hold the second flange, which not only complicates the structure, but also reduces the space for the spring and the power transmission part of the hub. Since the strength interferes with each other, the maximum twist angle of the damper disk is about 20 degrees to ensure strength.
本発明は上記問題に鑑み、上記従来のハブ分割
型のダンパーデイスクの形状をほとんど変えず、
又ハブの強度を抵下させることをなしに、捩り角
を45度程度まで大きくできる広捩り角ダンパーデ
イスクを提供することを目的とし、内周側フラン
ジの外歯と外周側フランジの内歯との間に円周方
向に長い遊びを設け、円筒状の第１ハブを略１周
にわたつて囲むように湾曲したリング状スプリン
グを、両フランジの両側にそれぞれ設け、各々の
リング状スプリングの一端を内周側フランジに係
合し、他端を外周側フランジに係合して初期状態
では前記遊びが略等しくなるように前記第１ハブ
を中心線に対して対称に両リング状スプリングを
配置し、外周側フランジの両側面に環状の摩擦板
を設け、この摩擦板をいずれか一方のサイドプレ
ートに連結した板ばねで外周側フランジの両側面
に圧接して外周側フランジを軸方向に保持するよ
うにしたことを特徴としている。 In view of the above problems, the present invention makes almost no changes to the shape of the conventional hub split type damper disk, and
In addition, the purpose is to provide a wide torsion angle damper disk that can increase the torsion angle to about 45 degrees without reducing the strength of the hub. Ring-shaped springs are provided on both sides of both flanges and are curved so as to surround the cylindrical first hub approximately once, with a long play in the circumferential direction between them, and one end of each ring-shaped spring both ring-shaped springs are arranged symmetrically with respect to the center line of the first hub so that the first hub is engaged with the inner circumference side flange and the other end is engaged with the outer circumference side flange so that the play is approximately equal in an initial state. An annular friction plate is provided on both sides of the outer flange, and a leaf spring connected to one of the side plates presses the friction plate against both sides of the outer flange to hold the outer flange in the axial direction. It is characterized by the fact that it is made to do so.
次に図面に基づいて本発明を説明する。第１図
は本発明を自動車用クラツチのクラツチデイスク
に採用した場合の縦断面図で、その−断面を
示す第３図の−線に沿う断面に相当してお
り、第２図は第３図の−線に沿う断面図であ
る。第１図において第１ハブ１は内周の内歯スプ
ライン２の部分で水平な出力側クラツチ軸（図示
せず）にスプライン嵌合しており、フランジ３
（内周側フランジ）を一体に有している。フラン
ジ３を囲み、それと同一厚さの外周側フランジ４
が第１図の同一垂直面上にあり、第３図のように
フランジ３の外周面に設けた外歯５が外周側フラ
ンジ４の内周面に設けた内歯６と円周方向の遊び
７，７′を隔てて噛み合つている。遊び７，７′は
比較的長く設定されており、両フランジ３，４は
遊び７，７′に対応する捩り角度範囲で回動自在
に嵌合している。両フランジ３，４は第３図の中
心線Ｏ１に対して上下対称に形成されており、外
歯５′および内歯６′（いずれも破線で図示する）
が形成されている。 Next, the present invention will be explained based on the drawings. FIG. 1 is a longitudinal cross-sectional view of the clutch disc of an automobile clutch in which the present invention is applied, and corresponds to the cross-section taken along the - line in FIG. 3, which shows the - cross section. It is a sectional view along the - line of. In FIG. 1, a first hub 1 is spline-fitted to a horizontal output side clutch shaft (not shown) at an internal spline 2 on the inner periphery, and a flange 3
(inner periphery side flange). An outer flange 4 surrounding the flange 3 and having the same thickness as the flange 3
are on the same vertical plane in FIG. 1, and as shown in FIG. 3, the outer teeth 5 provided on the outer peripheral surface of the flange 3 have play in the circumferential direction with the inner teeth 6 provided on the inner peripheral surface of the outer flange 4. 7 and 7' are interlocked. The plays 7, 7' are set to be relatively long, and both flanges 3, 4 are fitted to be rotatable within a torsion angle range corresponding to the plays 7, 7'. Both flanges 3 and 4 are vertically symmetrical with respect to the center line O1 in FIG. 3, and have external teeth 5' and internal teeth 6' (both shown by broken lines)
is formed.
下半部の外歯５′、内歯６′も同様であるが、上
半部の外歯５および内歯６を例に説明すると、外
歯５の内周側フランジ３の凹部８との間には半径
方向の〓間９が設けられている。又、内歯６とフ
ランジ３の凹部１０は摺動自在に当接して、外周
側フランジ４が第１ハブ１のフランジ３に回動自
在に嵌合している。 The same applies to the external teeth 5' and internal teeth 6' in the lower half, but to explain the external teeth 5 and internal teeth 6 in the upper half as an example, the relationship between the external teeth 5 and the recess 8 of the inner flange 3 is the same. A radial gap 9 is provided between them. Further, the inner teeth 6 and the recess 10 of the flange 3 are slidably abutted, and the outer peripheral side flange 4 is rotatably fitted into the flange 3 of the first hub 1.
第１図に示すように両フランジ３，４の両側に
は、円形断面を有するばね鋼線製のリング状スプ
リング１２，１５がそれぞれ設けられており、こ
のリング状スプリング１２，１５で詳しくは後述
するように両フランジ３，４を弾性的に連結して
いる。 As shown in FIG. 1, ring-shaped springs 12 and 15 made of spring steel wire and having a circular cross section are provided on both sides of both flanges 3 and 4, respectively. Both flanges 3 and 4 are elastically connected to each other in such a manner.
リング状スプリング１２は中心点Ｐ１（第１
図）を含む第３図中の第１ハブ１の中心線Ｏを中
心に略円弧状に湾曲した湾曲部５０と、湾曲部５
０から略接線状に伸びた直線部５１等からなり、
湾曲部５０に繋がる一端部５２をフランジ３の外
歯５に形成された孔１１に嵌合している。リング
状スプリング１２は一端部５２を孔１１に係止し
て、湾曲部５０は一端部５２から第３図で逆時計
回りに第１ハブ１の筒状部１３の周囲を略１周す
なわち点５３まで間隔を隔ててとり巻き、前記直
線部５１に連続している。直線部５１の端部は形
成されたスプリング１２の他端部５４は外周側フ
ランジ４の孔１４に係止している。このスプリン
グ１２は第１図の両フランジ３，４とリテイニン
グプレート２３との間に配置されている。 The ring-shaped spring 12 has a center point P1 (the first
A curved portion 50 curved in a substantially arc shape around the center line O of the first hub 1 in FIG.
Consisting of a straight line portion 51 extending approximately tangentially from 0,
One end 52 connected to the curved portion 50 is fitted into a hole 11 formed in the external teeth 5 of the flange 3. The ring-shaped spring 12 has one end 52 locked in the hole 11, and the curved part 50 extends around the cylindrical part 13 of the first hub 1 approximately once, that is, at a point, from the one end 52 counterclockwise in FIG. 53 at intervals, and continues to the straight portion 51. The other end 54 of the spring 12 formed at the end of the straight portion 51 is engaged with the hole 14 of the outer flange 4 . This spring 12 is arranged between both flanges 3, 4 and a retaining plate 23 in FIG.
一方、両フランジ３，４とクラツチプレート２
４との間にはリング状スプリング１５が配置され
ている。このスプリング１５も第３図に示すよう
にスプリング１２と同様に湾曲部５０′と直線部
５１′等からなり、一端部５２′を外歯５′の孔１
１′に係止して、孔１１′から逆時計回りに第１ハ
ブ１の筒状部１３の周囲を略１周、間隔を隔てて
とり巻き、直線部５１′の他端部５４′が外周側フ
ランジ４の孔１４′（第１図）に係止している。 On the other hand, both flanges 3 and 4 and clutch plate 2
A ring-shaped spring 15 is disposed between the spring 4 and the spring 15. As shown in FIG. 3, like the spring 12, this spring 15 also consists of a curved part 50', a straight part 51', etc., and one end 52' is connected to the hole of the external tooth 5'.
1', and wraps around the cylindrical part 13 of the first hub 1 counterclockwise from the hole 11' for approximately one turn at an interval, so that the other end 54' of the straight part 51' It is locked in a hole 14' (FIG. 1) of the outer flange 4.
したがつて、両スプリング１２，１５は第３図
の第１ハブ１の中心線Ｏ（第３図の紙面に直角）
を中心として点対称に設けられており、中心線Ｏ
回りの互いに逆方向に働く両スプリング１２，１
５のばね力で両フランジ３，４を弾性的に連結し
ている。これらのスプリング１２，１５のばね力
は略釣り合つており、クラツチデイスクが捩じら
れる前の初期状態では、第３図のように間〓７，
７′は略同一長さに保たれている。 Therefore, both springs 12 and 15 are aligned with the center line O of the first hub 1 in FIG. 3 (perpendicular to the plane of the paper in FIG. 3).
It is provided point symmetrically with the center line O
Both springs 12, 1 that work in opposite directions around the
Both flanges 3 and 4 are elastically connected by a spring force of 5. The spring forces of these springs 12 and 15 are approximately balanced, and in the initial state before the clutch disk is twisted, the gaps 7, 15 are as shown in FIG.
7' are kept approximately the same length.
フランジ３の両側面にはフリクシヨンワツシ
ヤ、等の摩擦材２２及び、コーンスプリング等の
押付部材２２′を介して、サイドプレート２１を
形成するリテイニングプレート２３とクラツチプ
レート２４とが、両プレート２３，２４の外周部
をストツプピン２５により互いに接近するように
連結一体化することによつて圧接している。外周
側フランジ４の同一円周上２箇所に設けられた切
欠窓２６（第３図）には、中心線が円周方向に延
びる姿勢で第１トーシヨンスプリング２７が縮設
され、切欠窓２６より張り出したスプリング２７
の部分は両プレート２３，２４に設けた窓孔２８
に嵌合している。切欠窓２６及び窓孔２８のデイ
スク円周方向両端の端面２６ａ，２８ａは第３図
に示す通常の中立時に円周上の位置が合致してお
り、従つてトーシヨンスプリング２７の両端面は
中立時に端面２６ａ，２８ａに圧接する。更に外
周側フランジ４には同一円周上２箇所に更に別の
２箇の切欠窓３０が設けてあり、この切欠窓３０
には第２トーシヨンスプリング３１が円周方向の
間隙３２，３２′を隔てて収容されている。切欠
窓３０より張り出したスプリング３１の部分は両
プレート２３，２４に設けた窓孔３３の端面３３
ａに圧接している。 On both sides of the flange 3, a retaining plate 23 and a clutch plate 24, which form the side plate 21, are attached via a friction material 22 such as a friction washer and a pressing member 22' such as a cone spring. The outer peripheries of 23 and 24 are connected and integrated by a stop pin 25 so as to approach each other, so that they are pressed into contact with each other. A first torsion spring 27 is compressed in the notch windows 26 (FIG. 3) provided at two locations on the same circumference of the outer periphery side flange 4 with the center line extending in the circumferential direction. More overhanging spring 27
The part marked with is the window hole 28 provided in both plates 23 and 24.
is fitted. The end surfaces 26a and 28a of the notch window 26 and the window hole 28 at both ends in the disk circumferential direction are aligned on the circumference in the normal neutral state shown in FIG. 3, and therefore both end surfaces of the torsion spring 27 are in the neutral state. At the same time, it comes into pressure contact with the end surfaces 26a and 28a. Furthermore, two other notched windows 30 are provided on the outer peripheral side flange 4 at two locations on the same circumference, and these notched windows 30
A second torsion spring 31 is housed in with a circumferential gap 32, 32' in between. The part of the spring 31 that protrudes from the cutout window 30 is located at the end surface 33 of the window hole 33 provided in both plates 23 and 24.
It is in pressure contact with a.
クラツチプレート２４の外周部には、半径方向
外方にクツシヨニングプレート３７を介してフエ
ーシング３８が、半径方向内方の第２ハブ４とク
ラツチプレート２４との間には板ばね３９がそれ
ぞれ設けられ、リベツト４０によつてクラツチプ
レート２４に一体的に固着されている。更に第２
図に示すように、外周側フランジ４の両側には摩
擦板４１が接着されており、摩擦板４１は夫々リ
テイニングプレート２３と、板ばね３９に圧接し
ている。フエーシング３８は図示されていないエ
ンジン側フライホイールとクラツチケース側プレ
ツシヤプレートに対向している。なおストツプピ
ン２５は外周側フランジ４の外周部に設けた切欠
３６に円周方向の間隙を隔てて配置されている。 A facing 38 is provided on the outer periphery of the clutch plate 24 radially outwardly via a cushioning plate 37, and a leaf spring 39 is provided radially inwardly between the second hub 4 and the clutch plate 24. and is integrally fixed to the clutch plate 24 by rivets 40. Furthermore, the second
As shown in the figure, friction plates 41 are bonded to both sides of the outer flange 4, and the friction plates 41 are in pressure contact with the retaining plate 23 and the leaf spring 39, respectively. The facing 38 faces a flywheel on the engine side and a pressure plate on the clutch case side, which are not shown. The stop pin 25 is disposed in a notch 36 provided on the outer periphery of the outer flange 4 with a gap in the circumferential direction.
次に作動を説明する。エンジンからの回転力を
車軸に伝達する場合は、デイスク外周のフエーシ
ング３８のフライホイールに圧接し、第１ハブ１
内のクラツチ軸から動力を取り出すのであるが、
説明の便宜上、仮にフエーシング３８を固定し、
第１ハブ１を矢印Ａ方向（第３図）に回動させた
場合を考える。外周側フランジ４が強い第１トー
シヨンスプリング２７により固定されているた
め、まずリング状スプリング１２が圧縮され同時
にスプリング１５も圧縮される。この時第１トー
シヨンスプリング２７にも力が加わるが、スプリ
ング１２，１５に比べてはるかに強いスプリング
を用いているため、スプリング２７の圧縮は無視
できる。第１ハブ１に加えた矢印Ａ方向のトルク
はフランジ３、リング状スプリング１２，１５、
外周側フランジ４、第１トーシヨンスプリング２
７、クラツチプレート２４、クツシヨニングプレ
ート３７を経てフエーシング３８に伝えられる。
１段目のスプリングとなるリング状スプリング１
２，１５としては充分柔らかいものを採用してい
るため、捩り角度の増加に対する捩りトルクの増
加は第４図T1のように僅かである。そして捩り
角度がθ1（実施例では32度に設定）になると外歯
５と内歯６の遊び７が０となり、外歯５が内歯６
に衝突し、フランジ３と第２ハブ４が一体化して
同一の動きをするようになり、第１トーシヨンス
プリング２７の圧縮が開始される（第４図T2）。
その後外周側フランジ４がθ2だけ回動すると、間
隙３２が０になり、切欠窓３０の端面３０ａが第
２トーシヨンスプリング３１の端面に衝突し、３
段目のスプリング３１の圧縮が始まり、外周側フ
ランジ４が回動し始めてから捩り角度がθ3になつ
たときストツプピン２５が切欠３６の端面３６ａ
に衝突してデイスク全体が一体化する。即ちその
時にデイスクの最大捩り角度が与えられる。一方
１段目のヒステリシスはフランジ３とサイドプレ
ート２１の間の摩擦材２２により発生し、２段目
及び３段目のヒステリシスは上記摩擦材２２に加
えて外周側フランジ４と板ばね３９、リテイニン
グプレート２３の間の摩擦板４１により発生す
る。そして２段目のヒステリシスは捩り特性の２
段目T2の立ち上り部分より発生する。最大捩り
角度迄捩れた後に捩り角度が減少する時の捩りト
ルクは第４図のT3′，T2′，T1′の線に沿い変化す
る。１段目のヒステリシスは十分小さいため第４
図ではT1，T1′を同一直線で示している。捩り角
度がマイナス側に変化する場合の特性は第４図の
左半分に示す通りにプラス側と略対称になる。 Next, the operation will be explained. When transmitting rotational force from the engine to the axle, the first hub 1 is pressed against the flywheel of the facing 38 on the outer periphery of the disk.
The power is extracted from the clutch shaft inside.
For convenience of explanation, it is assumed that the facing 38 is fixed,
Consider a case where the first hub 1 is rotated in the direction of arrow A (FIG. 3). Since the outer peripheral side flange 4 is fixed by the strong first torsion spring 27, the ring-shaped spring 12 is first compressed and the spring 15 is also compressed at the same time. At this time, force is also applied to the first torsion spring 27, but since the spring is much stronger than the springs 12 and 15, the compression of the spring 27 can be ignored. The torque applied to the first hub 1 in the direction of arrow A is applied to the flange 3, ring springs 12, 15,
Outer flange 4, first torsion spring 2
7, is transmitted to the facing 38 via the clutch plate 24 and cushioning plate 37.
Ring-shaped spring 1 which becomes the first stage spring
2 and 15 are sufficiently soft, the increase in torsion torque with respect to the increase in torsion angle is slight as shown in FIG. 4 T1 . When the torsion angle reaches θ 1 (set to 32 degrees in the example), the play 7 between the external teeth 5 and the internal teeth 6 becomes 0, and the external teeth 5 become the internal teeth 6.
, the flange 3 and the second hub 4 become integrated and move in the same manner, and the first torsion spring 27 starts to be compressed (T 2 in FIG. 4).
After that, when the outer peripheral side flange 4 rotates by θ 2 , the gap 32 becomes 0, the end face 30a of the notch window 30 collides with the end face of the second torsion spring 31, and the 3
When the spring 31 in the first stage starts to be compressed, the outer flange 4 starts to rotate, and the torsion angle reaches θ 3 , the stop pin 25 touches the end surface 36a of the notch 36.
It collides with the disk and the entire disk becomes one. That is, the maximum twist angle of the disk is then given. On the other hand, the first stage hysteresis is caused by the friction material 22 between the flange 3 and the side plate 21, and the second and third stage hysteresis is caused by the friction material 22, the outer flange 4 and the leaf spring 39, and the rest. This occurs due to the friction plate 41 between the inning plates 23. The second stage hysteresis is 2 of the torsional characteristics.
It occurs from the rising part of stage T2 . The torsion torque when the torsion angle decreases after being twisted to the maximum torsion angle changes along the lines T 3 ′, T 2 ′, and T 1 ′ in FIG. 4. Since the hysteresis of the first stage is sufficiently small, the hysteresis of the fourth stage is
In the figure, T 1 and T 1 ' are shown as the same straight line. The characteristics when the twist angle changes to the negative side are approximately symmetrical to the positive side, as shown in the left half of FIG.
以上説明したように本発明においては、内周側
フランジ３の外歯５と外周側フランジ４の内歯６
との間に円周方向に長い遊び７，７′を設け、円
筒状の第１ハブ１を略１周にわたつて囲むように
湾曲したリング状スプリング１２，１５を、両フ
ランジの両側にそれぞれ設け、各々のリング状ス
プリング１２，１５の一端を内周側フランジ３に
係合し、他端を外周側フランジ４に係合して、初
期状態では前記遊び７，７′が略等しくなるよう
に前記第１ハブ１の中心線Ｏに対して対称に両リ
ング状スプリング１２，１５を配置し、外周側フ
ランジ４の両側面に環状の摩擦板４１を設け、こ
の摩擦板４１をいずれか一方のサイドプレート２
４に連結して板ばね９で外周側フランジ４の両側
面に圧接して外周側フランジ４を軸方向に保持す
るようにしたので、従来のようにフランジ３に切
欠きや窓孔を設けたり、外周側フランジ４を挾持
するプレートを設ける必要がなくなり、構造が簡
単になるばかりでなく、切欠きや窓孔による第１
ハブ１の強度の低下がないので、遊び７，７′を
大きくとることができ、リング状スプリング１
２，１５で大きな捩り角度範囲にわたつてばね力
を発揮でき、衝撃吸収能力が向上する。又従来の
形状をほとんど変えずに製作でき、しかも捩り角
度45度程度迄大きく設定できるため、製作コスト
が低くかつ高能力のダンパーデイスクが得られる
利点がある。 As explained above, in the present invention, the outer teeth 5 of the inner flange 3 and the inner teeth 6 of the outer flange 4
A long play 7, 7' is provided in the circumferential direction between the cylindrical first hub 1 and ring-shaped springs 12, 15 which are curved so as to surround approximately one circumference of the cylindrical first hub 1 are provided on both sides of both flanges, respectively. One end of each ring-shaped spring 12, 15 is engaged with the inner flange 3, and the other end is engaged with the outer flange 4, so that the plays 7, 7' are approximately equal in the initial state. Both ring-shaped springs 12 and 15 are arranged symmetrically with respect to the center line O of the first hub 1, and an annular friction plate 41 is provided on both sides of the outer peripheral side flange 4, and this friction plate 41 is attached to either one of the sides. side plate 2
4, and the plate springs 9 are pressed against both sides of the outer flange 4 to hold the outer flange 4 in the axial direction. , there is no need to provide a plate to hold the outer flange 4, which not only simplifies the structure, but also allows the first
Since there is no decrease in the strength of the hub 1, the play 7, 7' can be increased, and the ring-shaped spring 1
2.15, the spring force can be exerted over a large torsion angle range, and the shock absorption ability is improved. Moreover, since it can be manufactured without changing the conventional shape and the twist angle can be set as large as about 45 degrees, there is an advantage that a damper disk with low manufacturing cost and high performance can be obtained.
なお実施例では、第２段目、第３段目のヒステ
リシスは、外周側フランジ４に接着した摩擦板４
１をリテイニングプレート２３と板ばね３９に圧
接させることによつて得られるようにしたため、
摩擦板４１が中心より離れた位置となり、大きな
ヒステリシスを容易に得られる利点がある。 In the embodiment, the second and third stage hysteresis is achieved by the friction plate 4 bonded to the outer flange 4.
1 can be obtained by pressing the retaining plate 23 and the leaf spring 39,
There is an advantage that the friction plate 41 is located away from the center, and a large hysteresis can be easily obtained.
第５図は別の実施例を示す第１図に対応する縦
断面図である。このようにフエーシングのないダ
ンパータイプで、クツシヨニングプレート３７が
クラツチプレート２４と一体に形成されている構
造のものでも本発明を採用することができる。 FIG. 5 is a longitudinal sectional view corresponding to FIG. 1 showing another embodiment. As described above, the present invention can also be applied to a damper type without facing, in which the cushioning plate 37 is formed integrally with the clutch plate 24.
なお本発明を具体化するにあたつて、最終段の
スプリングを充分強くしてストツプピン２５を省
略してもよい。又板ばね３９は、クツシヨニング
プレート３７を内方に延長することにより一体に
形成することもできる。このように構成すれば更
に構造が簡略化する利点がある。 In embodying the present invention, the stop pin 25 may be omitted by making the final stage spring sufficiently strong. The leaf spring 39 can also be formed integrally with the cushioning plate 37 by extending it inwardly. This configuration has the advantage of further simplifying the structure.
第１図は本発明を自動車用クラツチのクラツチ
デイスクに採用した場合の実施例を示す縦断面
図、第２図は実施例の別の部分を示す縦断面部分
図、第３図は第１図の−断面図、第４図は捩
り特性を示す図、第５図は別の実施例の第１図に
対応する縦断面図である。１……第１ハブ、４…
…外周側フランジ、５……外歯、６……内歯、
７，７′……遊び、１２，１５……リング状スプ
リング、２１……サイドプレート、２７，３１…
…トーシヨンスプリング。
FIG. 1 is a vertical sectional view showing an embodiment in which the present invention is applied to a clutch disk of an automobile clutch, FIG. 2 is a vertical sectional partial view showing another part of the embodiment, and FIG. 4 is a diagram showing torsional characteristics, and FIG. 5 is a longitudinal sectional view corresponding to FIG. 1 of another embodiment. 1...first hub, 4...
...outer flange, 5...external teeth, 6...internal teeth,
7, 7'... play, 12, 15... ring-shaped spring, 21... side plate, 27, 31...
...Torsion spring.
Claims (1)
環状板形の内周側フランジを有する第１ハブと、
内周側フランジの外歯に回転方向の遊びを隔てて
嵌合する内歯を有する外周側フランジと、両フラ
ンジの両側に配置された回動自在のサイドプレー
トと、外周側フランジとサイドプレートとの間に
挿入されたトーシヨンスプリングを有するダンパ
ーデイスクにおいて、内周側フランジ３の外歯５
と外周側フランジ４の内歯６との間に円周方向に
長い遊び７，７′を設け、円筒状の第１ハブ１を
略１周にわたつて囲むように湾曲したリング状ス
プリング１２，１５を、両フランジの両側にそれ
ぞれ設け、各々のリング状スプリング１２，１５
の一端を内周側フランジ３に係合し、他端を外周
側フランジ４に係合して、初期状態では前記遊び
７，７′が略等しくなるように前記第１ハブ１の
中心線Ｏに対して対称に両リング状スプリング１
２，１５を配置し、外周側フランジ４の両側面に
環状の摩擦板４１を設け、この摩擦板４１をいず
れか一方のサイドプレート２４に連結した板ばね
３９で外周側フランジ４の両側面に圧接して外周
側フランジ４を軸方向に保持するようにしたこと
を特徴とするダンパーデイスク。1. A first hub having spline internal teeth on the inner circumferential surface and a substantially annular plate-shaped inner circumferential flange on the outer circumferential surface;
an outer flange having internal teeth that fit into the outer teeth of the inner flange with rotational play, a rotatable side plate disposed on both sides of both flanges, and an outer flange and a side plate. In a damper disk having a torsion spring inserted between the outer teeth 5 of the inner flange 3
A ring-shaped spring 12 is provided with a long play 7, 7' in the circumferential direction between the inner teeth 6 of the outer flange 4, and is curved so as to surround the cylindrical first hub 1 over approximately one circumference. 15 are provided on both sides of both flanges, and each ring-shaped spring 12, 15
One end is engaged with the inner flange 3, the other end is engaged with the outer flange 4, and the center line O of the first hub 1 is adjusted so that the plays 7 and 7' are approximately equal in the initial state. Both ring-shaped springs 1 are symmetrical to
2 and 15, an annular friction plate 41 is provided on both sides of the outer flange 4, and a leaf spring 39 connecting this friction plate 41 to one of the side plates 24 is attached to both sides of the outer flange 4. A damper disk characterized in that the outer peripheral flange 4 is held in the axial direction by pressure contact.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP71482A JPS58118330A (en) | 1982-01-05 | 1982-01-05 | Damper disc |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP71482A JPS58118330A (en) | 1982-01-05 | 1982-01-05 | Damper disc |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58118330A JPS58118330A (en) | 1983-07-14 |
| JPH0155690B2 true JPH0155690B2 (en) | 1989-11-27 |
Family
ID=11481424
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP71482A Granted JPS58118330A (en) | 1982-01-05 | 1982-01-05 | Damper disc |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58118330A (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59159431A (en) * | 1983-02-28 | 1984-09-10 | Atsugi Motor Parts Co Ltd | Clutch disc |
| GB8316095D0 (en) * | 1983-06-11 | 1983-07-20 | Automotive Prod Plc | Friction clutch driven plate |
| JPS60142322U (en) * | 1984-03-01 | 1985-09-20 | アイシン精機株式会社 | clutch disc |
| GB8406198D0 (en) * | 1984-03-09 | 1984-04-11 | Automotive Prod Plc | Friction clutch driven plate |
| JPS62204018A (en) * | 1986-02-28 | 1987-09-08 | Hino Motors Ltd | Clutch disc |
| JPH07109220B2 (en) * | 1986-02-28 | 1995-11-22 | 日野自動車工業株式会社 | Clutch disc |
-
1982
- 1982-01-05 JP JP71482A patent/JPS58118330A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58118330A (en) | 1983-07-14 |
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