JPH0222498Y2 - - Google Patents
Info
- Publication number
- JPH0222498Y2 JPH0222498Y2 JP1984005890U JP589084U JPH0222498Y2 JP H0222498 Y2 JPH0222498 Y2 JP H0222498Y2 JP 1984005890 U JP1984005890 U JP 1984005890U JP 589084 U JP589084 U JP 589084U JP H0222498 Y2 JPH0222498 Y2 JP H0222498Y2
- Authority
- JP
- Japan
- Prior art keywords
- window
- disk
- torsion spring
- edge
- window hole
- 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
- 238000013459 approach Methods 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 description 6
- 239000000463 material Substances 0.000 description 3
- 238000009423 ventilation Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000005299 abrasion 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
- 230000006866 deterioration Effects 0.000 description 1
- 230000002542 deteriorative effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/62—Clutch-bands; Clutch shoes; Clutch-drums
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/644—Hub construction
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
【考案の詳細な説明】
（産業上の利用分野）
本考案は主として自動車等のクラツチデイスク
に好適な捩りダンパーデイスクに関する。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a torsion damper disk suitable mainly for clutch disks of automobiles and the like.
（従来技術）
中央のハブに形成された環状フランジの両側に
１対の環状サイドプレートを配置し、両サイドプ
レートとフランジの対向する位置にそれぞれ窓孔
を設け、各窓孔に略円周方向に延在するトーシヨ
ンスプリングを介在させてハブとサイドプレート
とを円周方向弾性的に連結する構成がダンパーデ
イスクとして一般に採用されている。又各サイド
プレートの窓孔の内、外周側両端縁には、それぞ
れスプリングをわずかに覆うように窓縁が一体に
形成されて、スプリングの抜止めを構成してい
る。それら窓縁のうち内周側の窓縁はフライホイ
ールやプレツシヤプレートの形状、或はダンパー
デイスクに多段ヒステリシス特性を発揮させるた
めに設けられるサブプレートの配置及び形状によ
つては、スペースの都合上省略される場合もあ
る。(Prior art) A pair of annular side plates are arranged on both sides of an annular flange formed on a central hub, and window holes are provided at positions where both side plates and the flange face each other. A structure in which a hub and a side plate are elastically connected in the circumferential direction by interposing a torsion spring extending in the damper disk is generally adopted as a damper disk. In addition, window edges are integrally formed on both edges of the inner and outer circumferential sides of the window holes of each side plate so as to slightly cover the springs to prevent the springs from coming off. The space on the inner edge of the window may vary depending on the shape of the flywheel and pressure plate, or the arrangement and shape of the sub-plate provided to make the damper disk exhibit multi-stage hysteresis characteristics. It may be omitted for convenience.
内周側の窓縁が省略されたサイドプレートを一
例として第１図に示す。第１図で明らかなよう
に、従来の窓縁５０は単に窓孔５１から平板状に
切り起こされているのみであり、強度を充分に確
保するのが難しい。即ちダンパーデイスク作動中
において窓孔５１に円周方向（矢印X1方向）に
嵌め込まれたトーシヨンスプリング（図示せず）
が遠心力を受けると、窓縁５０の基部５２の近傍
に亀裂が生じ易いという不具合を有している。そ
のため従来の構成では、サイドプレート５３の板
厚を必要以上に厚くしたり、又高価な材料を使用
する必要が生じ、重量アツプやコストアツプを招
いている。又窓孔５１円周方向端面はプレート５
３の板厚分の面積しか有しておらず、スプリング
（図示せず）の当接により早期に摩耗してしまう
不具合も有している。 FIG. 1 shows an example of a side plate in which the window edge on the inner peripheral side is omitted. As is clear from FIG. 1, the conventional window edge 50 is simply cut and raised from the window hole 51 into a flat plate shape, and it is difficult to ensure sufficient strength. That is, a torsion spring (not shown) fitted into the window hole 51 in the circumferential direction (arrow X 1 direction) while the damper disk is in operation.
When subjected to centrifugal force, cracks tend to form near the base 52 of the window edge 50, which is a problem. Therefore, in the conventional configuration, it is necessary to make the side plate 53 thicker than necessary or to use expensive materials, resulting in increased weight and cost. Further, the circumferential end surface of the window hole 51 is connected to the plate 5.
It has an area only equal to the thickness of the plate of 1.3 mm, and also has the problem of premature wear due to contact with a spring (not shown).
一方別の実施例として窓孔５１にスプリングを
完全に覆うカバーを一体に形成した構成が知られ
ているが、その場合には重量が大きくなり過ぎる
不具合を有するばかりでなく、通気性が悪くなつ
て放熱性能が劣化してしまう不具合も有してい
る。又上述したようにフライホイールやサブプレ
ートとの関係でスペース上の予裕がない場合には
採用することは不可能である。 On the other hand, as another example, a structure is known in which a cover that completely covers the spring is integrally formed in the window hole 51, but in that case, not only does the weight become too large, but also the ventilation becomes poor. It also has the problem of deteriorating heat dissipation performance. Moreover, as mentioned above, it is impossible to adopt this method if there is no space available due to the relationship with the flywheel and sub-plate.
（考案の目的）
(a) 通気性能の劣化を防ぎながら窓縁も含めた窓
孔の強度を向上させることにより、サイドプレ
ートの板厚を薄くできるようにして重量低減を
図り、材料変更を可能にしてコスト低減を図る
と共に、窓孔の耐摩耗性を向上させる。(Purpose of the invention) (a) By improving the strength of the window hole, including the window edge, while preventing deterioration of ventilation performance, the thickness of the side plate can be made thinner, reducing weight and making it possible to change the material. This reduces costs and improves the abrasion resistance of the window holes.
(b) フライホイールやサブプレートによつて窓孔
内周側に窓縁を形成する場所予裕がない場合で
も、窓孔の強度を向上できるようにする。(b) The strength of the window hole can be improved even when there is no space to form a window edge on the inner circumference side of the window hole using a flywheel or sub-plate.
（考案の構成）
中央のハブに形成された環状フランジの両側に
１対のサイドプレートを配置し、両サイドプレー
トとフランジの対向する位置にそれぞれ窓孔を設
け、各窓孔に略円周方向に延在するトーシヨンス
プリングを介在させてハブとサイドプレートとを
円周方向弾性的に連結した捩りダンパーデイスク
において、次の事項を必須の要件とする捩りダン
パーデイスクである。(Structure of the invention) A pair of side plates are arranged on both sides of an annular flange formed on the central hub, and window holes are provided at positions where both side plates and the flange face each other. This is a torsion damper disk in which a hub and a side plate are elastically connected in the circumferential direction with a torsion spring extending in between, and the torsion damper disk has the following essential requirements.
(a) サイドプレートに形成された上記窓孔の外周
縁に、トーシヨンスプリングのデイスク外周側
部分のみを覆う窓縁を一体に形成する。(a) A window edge that covers only the outer circumferential portion of the disk of the torsion spring is integrally formed on the outer circumferential edge of the window hole formed in the side plate.
(b) 窓孔及び窓縁のデイスク円周方向両端縁間に
トーシヨンスプリング受座を一体に形成する。(b) A torsion spring seat is integrally formed between the window hole and the window edge in the circumferential direction of the disk.
(c) 窓縁のデイスク半径方向の長さを上記トーシ
ヨンスプリング受座よりも短く設定する。(c) Set the length of the window edge in the radial direction of the disk to be shorter than the torsion spring seat.
(d) トーシヨンスプリング受座の形状を、デイス
ク半径方向内周側へ行くにつれて窓孔に接近す
る凹曲面状に形成する。(d) The shape of the torsion spring seat is formed into a concave curved shape that approaches the window hole as it goes toward the inner circumferential side in the radial direction of the disk.
（実施例）
第２図は本考案によるダンパーデイスクを自動
車用クラツチデイスクに採用した場合を示してい
る。第２図において、O1−O1を中心とするスプ
ラインハブ１は出力軸（図示せず）に嵌合するス
プライン２を内周面に備え、外周面に環状フラン
ジ３を一体に備えている。フランジ３の両側面内
周部に沿つて環状にヒステリシストルク発生部
４，５が配置され、トルク発生部４，５を挾んで
フランジ３の両側には１対の環状サイドプレート
６，７（クラツチプレートとリテイニングプレー
ト）が配置されている。フランジ３及び両プレー
ト６，７の外周寄りの部分にはそれぞれ複数個の
窓孔９，１０，１１（各１個のみ図示）がクラツ
チデイスクの円周方向に間隔を隔てて設けられ、
各３個１組の窓孔９，１０，１１は中心線O1−
O1方向に対向し、各組の窓孔９，１０，１１に
は圧縮コイルスプリング１２（トーシヨンスプリ
ングの一例）が嵌まつている。各スプリング１２
はクラツチデイスクの円周方向に延びており、フ
ランジ３と両プレート６，７はスプリング１２に
よりデイスク円周方向弾性的に連結されている。
両プレート６，７の外周部は、フランジ３外周部
の切欠き３ａにデイスク円周方向の遊びを有して
嵌合するストツプピン８によつて互いに一体的に
連結されている。一方のプレート６（クラツチプ
レート）の外周部にはクツシヨニングプレート１
３の内周部が固定され、プレート１３の両面には
環状のフエーシング１４が固定されている。フエ
ーシング１４は図示しないエンジン側のフライホ
イールとプレツシヤプレートとの狭間に配置され
ている。(Embodiment) FIG. 2 shows a case where the damper disk according to the present invention is applied to a clutch disk for an automobile. In Fig. 2, a spline hub 1 centered at O 1 - O 1 has a spline 2 on its inner circumferential surface that fits into an output shaft (not shown), and an annular flange 3 on its outer circumferential surface. . Hysteresis torque generating parts 4 and 5 are arranged annularly along the inner periphery of both sides of the flange 3, and a pair of annular side plates 6 and 7 (clutches) are arranged on both sides of the flange 3, sandwiching the torque generating parts 4 and 5. plate and retaining plate) are arranged. A plurality of window holes 9, 10, 11 (only one of each is shown) are provided at intervals in the circumferential direction of the clutch disk in the portions of the flange 3 and both plates 6, 7 near the outer periphery, respectively.
Each set of three window holes 9, 10, 11 has a center line O 1 −
A compression coil spring 12 (an example of a torsion spring) is fitted into each set of window holes 9, 10, 11 facing in the O1 direction. Each spring 12
extends in the circumferential direction of the clutch disk, and the flange 3 and both plates 6, 7 are elastically connected in the disk circumferential direction by a spring 12.
The outer peripheries of both plates 6 and 7 are integrally connected to each other by a stop pin 8 that fits into a notch 3a on the outer periphery of the flange 3 with play in the disk circumferential direction. A cushioning plate 1 is attached to the outer periphery of one plate 6 (clutch plate).
The inner peripheral portion of plate 13 is fixed, and annular facings 14 are fixed to both sides of plate 13. The facing 14 is arranged between a flywheel and a pressure plate on the engine side (not shown).
サイドプレート６の窓孔１０には第３図に示す
ように、外周側のみに窓縁２０が一体に形成さ
れ、窓縁２０がスプリング１２（第２図）のデイ
スク外周側部分を覆うことによつてスプリング１
２が飛び出さないようになつている。更に窓縁２
０及び窓孔１０のデイスク円周方向両端縁間には
スプリング１２の受座２１，２２が一体に形成さ
れている。一方第２図のサイドプレート７の窓孔
１１も外周側は窓孔１０と同様の構成が採用され
ており、窓縁２３及び受座２４が一体に形成され
ている。なお、プレート７側はスペース上の予裕
があることから、窓孔１１の内周側には従来と同
様に切り起こされて形成された窓縁２５が一体に
形成されている。又これらサイドプレート６，７
は共にプレス成形によつて作られている。 As shown in FIG. 3, the window hole 10 of the side plate 6 is integrally formed with a window edge 20 only on the outer circumferential side, and the window edge 20 covers the outer circumferential portion of the disk of the spring 12 (FIG. 2). Yotsute spring 1
2 does not pop out. Furthermore, window sill 2
Seats 21 and 22 for the spring 12 are integrally formed between both ends of the disk circumferential direction of the window hole 10 and the disk circumferential direction. On the other hand, the window hole 11 of the side plate 7 shown in FIG. 2 also has the same structure as the window hole 10 on the outer peripheral side, and the window edge 23 and the seat 24 are integrally formed. In addition, since there is a space margin on the plate 7 side, a window edge 25 is integrally formed on the inner peripheral side of the window hole 11 by being cut and raised in the same manner as in the prior art. Also, these side plates 6, 7
Both are made by press molding.
次に作動を説明する。図示しないプレツシヤプ
レートによりフエーシング１４をエンジンのフラ
イホイールに押圧すると、フライホイールからト
ルクがフエーシング１４、プレート１３、プレー
ト６，７、スプリング１２、フランジ３、ハブ１
を介して出力軸に伝達される。その場合に、ハブ
１に対しフエーシング１４に加わる捩りトルクに
対応してスプリング１２が圧縮され、、両サイド
プレート６，７がフランジ３に対して捩れるの
で、トルク発生部４，５に滑りが生じる。その滑
りにより捩りトルク一捩り角特性中にヒステリシ
ストルクが発生し、該ヒステリシストルクにより
トルク振動が吸収されて、動力伝達機構の異常振
動や異音が防止される。 Next, the operation will be explained. When the facing 14 is pressed against the flywheel of the engine by a pressure plate (not shown), torque is applied from the flywheel to the facing 14, the plate 13, the plates 6 and 7, the spring 12, the flange 3, and the hub 1.
is transmitted to the output shaft via. In that case, the spring 12 is compressed in response to the torsional torque applied to the facing 14 relative to the hub 1, and both side plates 6, 7 are twisted relative to the flange 3, so that the torque generating parts 4, 5 are prevented from slipping. arise. Due to the slippage, hysteresis torque is generated during the torsion torque and torsion angle characteristic, and torque vibration is absorbed by the hysteresis torque, thereby preventing abnormal vibrations and abnormal noises of the power transmission mechanism.
ここでデイスクが中心線O1−O1を中心に高速
で回転することにより、スプリング１２が遠心力
を受けて窓縁２０，２３を外周側に押圧するが、
この場合は一体に形成された受座２１，２４，２
２によつて窓縁２０，２３が補強されており、サ
イドプレート６，７に亀裂が生じることはない。
又サイドプレート６，７とフランジ３間で捩れが
生じる毎に、スプリング１２が圧縮されて窓孔１
０，１１を強く押圧するが、受座２１，２４，２
２が形成されているので、窓孔１０，１１の早期
摩耗は防止される。 Here, as the disk rotates at high speed around the center line O 1 −O 1 , the spring 12 receives centrifugal force and presses the window edges 20 and 23 toward the outer periphery.
In this case, the seats 21, 24, 2 are integrally formed.
2, the window edges 20, 23 are reinforced, and no cracks will occur in the side plates 6, 7.
Also, each time a twist occurs between the side plates 6, 7 and the flange 3, the spring 12 is compressed and the window hole 1 is compressed.
0 and 11 strongly, but the catch seats 21, 24, 2
2 is formed, early wear of the window holes 10 and 11 is prevented.
（考案の効果）
サイドプレート６，７に形成された窓孔１０，
１１の外周縁に、トーシヨンスプリング１２のデ
イスク外周側部分のみを覆う窓縁２０，２３を一
体に形成すると共に、窓孔１０，１１及び窓縁２
０，２３のデイスク円周方向両端縁間にトーシヨ
ンスプリング１２の受座２１，２２，２４を一体
に形成したので；
(a) 通気性能の劣化を防ぎながら窓縁２１，２
２，２４も含めた窓孔１０，１１の強度の向上
が図れることから、サイドプレート６，７の板
厚を薄くして重量低減を図り、材料変更による
コスト低減が可能になると共に、窓孔１０，１
１の耐摩耗性が向上する。(Effect of the invention) Window holes 10 formed in the side plates 6, 7,
11 are integrally formed with window edges 20 and 23 that cover only the disk outer peripheral side of the torsion spring 12, and the window holes 10 and 11 and the window edge 2 are integrally formed.
Since the seats 21, 22, 24 of the torsion spring 12 are integrally formed between both ends of the disks 0, 23 in the circumferential direction;
Since it is possible to improve the strength of the window holes 10 and 11 including the window holes 2 and 24, it is possible to reduce the weight by reducing the thickness of the side plates 6 and 7, and to reduce costs by changing the material. 10,1
The wear resistance of No. 1 is improved.
(b) フライホイールやサブプレートによつて窓孔
１０，１１の内周側に窓縁を形成する場合的余
裕がない場合にでも、窓孔１０，１１の強度を
向上させることができる。(b) The strength of the window holes 10, 11 can be improved even when there is no room to form a window edge on the inner peripheral side of the window holes 10, 11 using a flywheel or a sub-plate.
(c) さらに本考案によると、窓縁２０，２３のデ
イスク半径方向長さを上記トーシヨンスプリン
グ受座２１，２２，２４よりも短く設定すると
共にトーシヨンスプリング受座２１，２２，２
４の形状を、第２図に示すようにデイスク半径
方向内周側へ行くにつれて窓孔１０，１１に接
近する凹曲面状に形成しているので、受座２
１，２２，２４を窓縁２０，２３と同程度の幅
に設定した構造よりも一層軽量化を図ることが
でき、しかも通風性も格段に向上する。また窓
縁２０，２３のデイスク半径方向の長さを上記
受座２１，２２，２４よりも短く設定すると共
に受座２１，２２，２４の形状を、デイスク半
径方向内周側へ行くにつれて窓孔１０，１１に
接近する凹曲面状に形成することにより、窓縁
２０，２３及び受座２１，２２，２４の軸方向
の張り出し量を一層小さくまとめることがで
き、その分クラツチの小型化を一層促進するこ
とができる。(c) Furthermore, according to the present invention, the length of the window edges 20, 23 in the disk radial direction is set shorter than the torsion spring seats 21, 22, 24, and the torsion spring seats 21, 22, 2
4 is formed into a concave curved shape that approaches the window holes 10 and 11 toward the inner circumference in the radial direction of the disk, as shown in FIG.
It is possible to achieve further weight reduction than a structure in which widths 1, 22, and 24 are set to be approximately the same as the widths of window edges 20 and 23, and ventilation is also significantly improved. In addition, the length of the window edges 20, 23 in the disk radial direction is set shorter than that of the seats 21, 22, 24, and the shapes of the seats 21, 22, 24 are changed as they move toward the inner circumferential side in the radial direction of the disk. 10, 11, the amount of axial protrusion of the window edges 20, 23 and seats 21, 22, 24 can be further reduced, and the clutch can be further miniaturized. can be promoted.
第１図は従来のダンパーデイスクの斜視部分
図、第２図は本考案によるダンパーデイスクの縦
断面部分図、第３図はサイドプレートの斜視部分
図である。
１……ハブ、３……フランジ、６，７……サイ
ドプレート、１０，１１……窓孔、１２……トー
シヨンスプリング、２０，２３……窓縁、２１，
２２，２４……受座。
FIG. 1 is a partial perspective view of a conventional damper disk, FIG. 2 is a partial vertical cross-sectional view of the damper disk according to the present invention, and FIG. 3 is a partial perspective view of a side plate. 1... Hub, 3... Flange, 6, 7... Side plate, 10, 11... Window hole, 12... Torsion spring, 20, 23... Window edge, 21,
22, 24...Ukeza.
Claims (1)
１対の環状サイドプレートを配置し、両サイドプ
レートとフランジの対向する位置にそれぞれ窓孔
を設け、各窓孔に略円周方向に延在するトーシヨ
ンスプリングを介在させてハブとサイドプレート
とを円周方向弾性的に連結した捩りダンパーデイ
スクにおいて、サイドプレートに形成された上記
窓孔の外周縁に、トーシヨンスプリングのデイス
ク外周側部分のみを覆う窓縁を一体に形成すると
共に、窓孔及び窓縁のデイスク円周方向両端縁間
にトーシヨンスプリング受座を一体に形成し、上
記窓縁のデイスク半径方向の長さを上記トーシヨ
ンスプリング受座よりも短く設定すると共にトー
シヨンスプリング受座の形状を、デイスク半径方
向内周側へ行くにつれて窓孔に接近する凹曲面状
に形成したことを特徴とする捩りダンパーデイス
ク。 A pair of annular side plates are arranged on both sides of an annular flange formed on the central hub, and window holes are provided at positions where both side plates and the flange face each other, and each window hole extends approximately in the circumferential direction. In a torsion damper disk in which a hub and a side plate are elastically connected in the circumferential direction with a torsion spring interposed, only the outer circumferential portion of the disk of the torsion spring is attached to the outer circumferential edge of the window hole formed in the side plate. A window edge to be covered is integrally formed, and a torsion spring seat is integrally formed between the window hole and both ends of the window edge in the disk circumferential direction, and the length of the window edge in the disk radial direction is equal to the torsion spring. A torsion damper disk characterized in that the torsion spring catch is set to be shorter than the catch and the shape of the torsion spring catch is formed into a concave curved shape that approaches a window hole toward the inner circumference in the radial direction of the disk.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984005890U JPS60118029U (en) | 1984-01-19 | 1984-01-19 | Torsional damper disc |
| KR1019850000156A KR870001175B1 (en) | 1984-01-19 | 1985-01-09 | Damper disc |
| FR858500518A FR2558550B1 (en) | 1984-01-19 | 1985-01-15 | TORSION SHOCK ABSORBER DISC FOR MOTOR VEHICLE CLUTCH |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984005890U JPS60118029U (en) | 1984-01-19 | 1984-01-19 | Torsional damper disc |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60118029U JPS60118029U (en) | 1985-08-09 |
| JPH0222498Y2 true JPH0222498Y2 (en) | 1990-06-18 |
Family
ID=11623485
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1984005890U Granted JPS60118029U (en) | 1984-01-19 | 1984-01-19 | Torsional damper disc |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS60118029U (en) |
| KR (1) | KR870001175B1 (en) |
| FR (1) | FR2558550B1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2678337A1 (en) * | 1991-06-25 | 1992-12-31 | Valeo | TORSION DAMPER DEVICE, IN PARTICULAR FOR AUTOMOTIVE VEHICLES. |
| DE4327574C5 (en) * | 1992-10-09 | 2005-05-19 | Zf Sachs Ag | Torsionsdämpferscheibe |
| JP3052279B2 (en) * | 1994-11-11 | 2000-06-12 | 株式会社エクセディ | Clutch disk assembly and plate member thereof |
| JP3363302B2 (en) * | 1996-02-16 | 2003-01-08 | 株式会社エクセディ | Plate member of damper disk assembly |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5548893U (en) * | 1978-09-27 | 1980-03-31 | ||
| JPS55112424A (en) * | 1979-02-21 | 1980-08-30 | Fichtel & Sachs Ag | Clutch plate |
| JPS5779330A (en) * | 1980-09-04 | 1982-05-18 | Laycock Eng Ltd | Driven frictional clutch plate |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2115819A (en) * | 1933-05-22 | 1938-05-03 | Spicer Mfg Corp | Vibration dampener |
| US3799309A (en) * | 1972-07-10 | 1974-03-26 | Borg Warner | Clutch driven member assembly with vibration damper |
| JPS5548893Y2 (en) * | 1976-09-08 | 1980-11-14 | ||
| US4254855A (en) * | 1979-06-18 | 1981-03-10 | Dana Corporation | Coaxial spring damper drive |
-
1984
- 1984-01-19 JP JP1984005890U patent/JPS60118029U/en active Granted
-
1985
- 1985-01-09 KR KR1019850000156A patent/KR870001175B1/en active Pre-grant Review Request
- 1985-01-15 FR FR858500518A patent/FR2558550B1/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5548893U (en) * | 1978-09-27 | 1980-03-31 | ||
| JPS55112424A (en) * | 1979-02-21 | 1980-08-30 | Fichtel & Sachs Ag | Clutch plate |
| JPS5779330A (en) * | 1980-09-04 | 1982-05-18 | Laycock Eng Ltd | Driven frictional clutch plate |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2558550A1 (en) | 1985-07-26 |
| KR850005562A (en) | 1985-08-26 |
| KR870001175B1 (en) | 1987-06-16 |
| JPS60118029U (en) | 1985-08-09 |
| FR2558550B1 (en) | 1990-10-12 |
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