JPH0368245B2 - - Google Patents
Info
- Publication number
- JPH0368245B2 JPH0368245B2 JP58014291A JP1429183A JPH0368245B2 JP H0368245 B2 JPH0368245 B2 JP H0368245B2 JP 58014291 A JP58014291 A JP 58014291A JP 1429183 A JP1429183 A JP 1429183A JP H0368245 B2 JPH0368245 B2 JP H0368245B2
- Authority
- JP
- Japan
- Prior art keywords
- plate
- hub
- sub
- damping means
- friction
- 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
- 238000013016 damping Methods 0.000 claims description 42
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 230000006835 compression Effects 0.000 description 38
- 238000007906 compression Methods 0.000 description 38
- 230000000694 effects Effects 0.000 description 5
- 238000010521 absorption reaction Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 2
- 239000000843 powder Substances 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000002245 particle 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
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】
産業上の利用分野
この発明は、自動車の動力伝達装置等に使用さ
れるクラツチデイスクに関する。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a clutch disk used in a power transmission device of an automobile or the like.
従来の技術
クラツチデイスクは、エンジン等のトルク変動
によつて生ずる捩じり振動を有効に吸収して、動
力伝達系に好ましくない振動或いは騒音などが生
ずるのを防止するためのものである。そして、こ
のクラツチデイスクは、小さな入力トルク域に対
しては低い捩じり剛性として変位を大きくして吸
振効果を高め、大きなトルクに対しては高い剛性
をもつて十分なトルク伝達を行い得るような特性
が望まれ、同時に、摩擦減衰能もそのトルクに対
して比例的に変化する特性が望まれる。2. Description of the Related Art A clutch disk is used to effectively absorb torsional vibrations caused by torque fluctuations of an engine, etc., and to prevent undesirable vibrations or noise from occurring in a power transmission system. This clutch disc has low torsional rigidity for small input torque ranges and increases displacement to increase the vibration absorption effect, and has high rigidity for large torques to ensure sufficient torque transmission. At the same time, it is desired that the friction damping ability changes proportionally to the torque.
そこで、この種のクラツチデイスクとして、例
えば、特開昭57−57924号公報或いは特開昭57−
134019号公報に示されるように、ハブのプレート
部とドライブプレートとの間に摩擦減衰手段の作
用制御を司るサブプレートを設け、このサブプレ
ートの両側に摩擦減衰手段を配置した構成のもの
が知られている。 Therefore, as this type of clutch disk, for example, Japanese Patent Application Laid-Open No. 57-57924 or Japanese Patent Application Laid-Open No. 57-57
As shown in Japanese Patent No. 134019, a sub-plate for controlling the operation of friction damping means is provided between the plate portion of the hub and the drive plate, and friction damping means are arranged on both sides of this sub-plate. It is being
発明が解決しようとする課題
しかしながら、この従来例にあつては、サブプ
レートがハブのボス部外周に直接支持されるよう
になつているため、この部分での摺動抵抗や摩耗
等が発生し、本来摩擦減衰手段で得られるべき所
期する摩擦減衰能が得られなくなる場合があつ
た。Problems to be Solved by the Invention However, in this conventional example, since the sub-plate is directly supported on the outer periphery of the boss portion of the hub, sliding resistance and wear occur at this portion. In some cases, the desired friction damping ability that should originally be obtained by the friction damping means cannot be obtained.
課題を解説するための手段
そこでこの発明は、ボス部とプレート部とを有
するハブと、このハブに対して相対回動可能に連
繋されたドライブプレートと、前記ハブのプレー
ト部とドライブプレートとの間に設けられ、摩擦
減衰手段の作用制御を司るサブプレートと、この
サブプレートと前記ハブプレート部との間に介装
された第１の摩擦減衰手段と、前記サブプレート
とドライブプレートとの間に介装された第２の摩
擦減衰手段とを備えたクラツチデイスクにおい
て、前記第１の摩擦減衰手段の摩擦力を前記第２
の摩擦減衰手段の摩擦力よりも小さくすると共
に、前記サブプレートの内周部に、ハブのボス部
の外周に沿つて筒状のベアリング受部を形成し、
このサブプレートを前記受部の内周側に設けたベ
アリングを介してハブのボス部外周に取り付けた
構成にしてある。Means for Explaining the Problem Therefore, the present invention provides a hub having a boss portion and a plate portion, a drive plate connected to the hub so as to be rotatable relative to the hub, and a connection between the plate portion of the hub and the drive plate. a sub-plate that is provided between and controls the action of the friction damping means; a first friction damping means that is interposed between the sub-plate and the hub plate; and between the sub-plate and the drive plate. and a second friction damping means interposed in the clutch disk, wherein the friction force of the first friction damping means is applied to the second friction damping means.
a cylindrical bearing receiving part is formed on the inner peripheral part of the sub-plate along the outer periphery of the boss part of the hub,
This sub-plate is attached to the outer periphery of the boss portion of the hub via a bearing provided on the inner periphery side of the receiving portion.
作 用
ハブとドライブプレートとの相対回動時に、サ
ブプレートはハブとの間で滑らかに回動して、摩
擦減衰手段の作用開始を円滑に制御する。Operation When the hub and drive plate rotate relative to each other, the sub-plate rotates smoothly between the hub and the drive plate, thereby smoothly controlling the start of the action of the friction damping means.
実施例
以下、この発明の実施例を図面と共に詳述す
る。Embodiments Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
図において、１はボス部１ａとプレート部１ｂ
とを有するハブである。このハブに対して相対回
動可能に連繋されるドライブプレートは、この実
施例ではプレート部１ｂの両側に一対として設け
られ、符番２，２′が付されている。後述する摩
擦減衰手段の作用制御を司るサブプレートもまた
この実施例で一対として設けられ、符番１４，１
４が付されている。該サブプレート１４と前記ハ
ブ１のプレート部１ｂには、第１段階で作用する
圧縮ばね３を収容する窓６，７を円周方向同一幅
をもつて形成し、これら窓６，７に第１段階で作
用する圧縮ばね３を収容してある。前記ドライブ
プレート２，２′とサブプレート１４，１４及び
ハブ１のプレート部１ｂには、第２段階以後で作
用する圧縮ばね４，５を収容する窓８，９，１
０，１１，２０，２１が形成してある。これら窓
のうちハブ１の窓９，１１はドライブプレート
２，２′の窓８，１０及びサブプレート１４，１
４の窓２０，２１よりも円周方向幅広に形成さ
れ、かつドライブプレート２，２′の窓８，１０
に対応するサブプレート１４，１４の窓２０，２
１の少なくとも一つは互いに円周方向同一幅をも
つて形成されていて、これら窓８，９，１０，１
１，２０，２１にそれぞれ第２、第３段階で作用
する圧縮ばね４，５を収容してある。前記ハブ１
のプレート部１ｂとサブプレート１４の間には第
１の摩擦減衰手段たる低摩擦部材１６を介在さ
せ、更に前記サブプレート１４とドライブプレー
ト２，２′の間には第２の摩擦減衰手段たる高摩
擦部材１７を介在してある。 In the figure, 1 indicates a boss portion 1a and a plate portion 1b.
It is a hub with In this embodiment, drive plates connected to the hub so as to be rotatable relative to each other are provided as a pair on both sides of the plate portion 1b, and are numbered 2 and 2'. A pair of sub-plates in charge of controlling the operation of the friction damping means described later are also provided in this embodiment, and are designated by reference numerals 14 and 1.
4 is attached. The sub-plate 14 and the plate portion 1b of the hub 1 are formed with windows 6 and 7 having the same width in the circumferential direction for accommodating the compression spring 3 that acts in the first stage. A compression spring 3 acting in one stage is accommodated. The drive plates 2, 2', the sub-plates 14, 14, and the plate portion 1b of the hub 1 are provided with windows 8, 9, 1 for accommodating compression springs 4, 5 that act after the second stage.
0, 11, 20, 21 are formed. Among these windows, the windows 9, 11 of the hub 1 are the windows 8, 10 of the drive plates 2, 2' and the sub-plates 14, 1.
The windows 8, 10 of the drive plates 2, 2' are formed wider in the circumferential direction than the windows 20, 21 of the drive plates 2, 2'.
Windows 20, 2 of sub-plates 14, 14 corresponding to
At least one of the windows 8, 9, 10, 1 is formed to have the same width in the circumferential direction.
1, 20 and 21 house compression springs 4 and 5 which act in the second and third stages, respectively. Said hub 1
A low friction member 16, which is a first friction damping means, is interposed between the plate portion 1b and the sub-plate 14, and a low friction member 16, which is a second friction damping means, is interposed between the sub-plate 14 and the drive plates 2, 2'. A high friction member 17 is interposed.
図面に示す実施例においてサブプレート１４
は、ハブ１のプレート部１ｂと両方のドライブプ
レート２，２′の間にあつて、このうちの一方の
サブプレート１４の内周部にはハブ１のボス部１
ａの外周に沿つて筒状のベアリング受部１４ａが
形成されていて、このサブプレート１４はベアリ
ング受部１４ａの内周に取り付けたベアリング１
５を介して、前記ボス部１ａ外周に回動自在に取
り付けられている。また、一方のサブプレート１
４と他方のサブプレート１４は一体的に回動する
ように、前記ハブのプレート部１ｂとの間に低摩
擦部材１６とばね定数の小さい皿ばね１６ａとを
挟持してピン１８によつて連結されている。そし
て該ピン１８は所望の遊び角度θをもつてハブ１
のプレート部１ｂと係合するように該プレート部
１ｂに設けた円弧状のピン受孔１９に挿入されて
いる。第３図はピン１８とピン受孔１９等の関係
を明確に示す展開断面図で、ピン１８とピン受孔
１９の一端の間には前記遊び角度θに相当する遊
び間〓G1が設けられている。 In the embodiment shown in the drawings, the sub-plate 14
is located between the plate portion 1b of the hub 1 and both drive plates 2, 2', and the boss portion 1 of the hub 1 is located on the inner peripheral portion of one of the sub-plates 14.
A cylindrical bearing receiving part 14a is formed along the outer periphery of the bearing part 14a, and this sub-plate 14 supports the bearing 1 attached to the inner periphery of the bearing receiving part 14a.
5, it is rotatably attached to the outer periphery of the boss portion 1a. Also, one sub-plate 1
4 and the other sub-plate 14 are connected by a pin 18 with a low-friction member 16 and a disc spring 16a having a small spring constant sandwiched between the plate portion 1b of the hub and the other sub-plate 14 so as to rotate together. has been done. Then, the pin 18 is attached to the hub 1 with a desired play angle θ.
It is inserted into an arc-shaped pin receiving hole 19 provided in the plate portion 1b so as to engage with the plate portion 1b. FIG. 3 is a developed sectional view that clearly shows the relationship between the pin 18 and the pin receiving hole 19, etc., and there is a clearance G 1 between the pin 18 and one end of the pin receiving hole 19, which corresponds to the play angle θ. It is being
また第１段階で作用する圧縮ばね３を収容する
窓６，７は、サブプレート１４，１４とハブ１の
プレート部１ｂの直径方向に対向する位置に円周
方向同一幅に形成されていて、これら窓６，７内
に圧縮ばね３が所望の初期荷重をもつべく、長さ
L1に圧縮された状態で収容されている。また第
２段階で作用する圧縮ばね４を収容する窓８，９
は、ドライブプレート２，２′に形成される窓８
よりもハブ１のプレート部１ｂに形成される窓９
が大きくなるようになつていて、これら窓８，９
内に圧縮ばね４が所望の初期荷重をもつべく、長
さL2に圧縮された状態で収容されていると共に
該圧縮ばね４と前記ハブ１のプレート部１ｂに形
成した窓９の一端縁の間には前記窓８，９の寸法
差によつて前記遊び間〓G1と略等しい遊び間〓
G2が設けられている。また第３段階で作用する
圧縮ばね５を収容する窓１０，１１は、ドライブ
プレート２，２′とハブ１のプレート部１ｂに、
前記窓８，９の寸法差よりも更に大きな寸法差を
もつて形成されていて、これら窓１０，１１内に
圧縮ばね５は所望の初期荷重を持つべく、長さ
L3に圧縮された状態で収容されていると共に該
圧縮ばね５と前記ハブ１のプレート部１ｂに形成
した窓１１の一端縁の間には前記寸法差によつて
前記遊び間〓G2よりも大きい遊び間〓G3が設け
られている。G4はドライブプレート２，２′を結
合しているピン１３のストローク許容用〓間であ
る。 Further, the windows 6 and 7 that house the compression springs 3 that act in the first stage are formed with the same width in the circumferential direction at positions facing each other in the diametrical direction of the sub-plates 14 and 14 and the plate portion 1b of the hub 1. In order for the compression spring 3 to have the desired initial load in these windows 6 and 7,
It is housed in a compressed state in L 1 . The windows 8, 9 also house the compression springs 4 which act in the second stage.
is a window 8 formed in the drive plates 2, 2'.
The window 9 formed in the plate portion 1b of the hub 1
is getting larger, and these windows 8 and 9
A compression spring 4 is accommodated in a compressed state with a length L 2 so as to have a desired initial load. Due to the dimensional difference between the windows 8 and 9, there is a clearance approximately equal to the clearance G1 .
G2 is provided. Further, windows 10 and 11 that house the compression springs 5 that act in the third stage are provided in the drive plates 2 and 2' and the plate portion 1b of the hub 1.
The windows 8 and 9 are formed with a larger dimensional difference than that of the windows 8 and 9, and the compression spring 5 in these windows 10 and 11 has a length so as to have a desired initial load.
L 3 is housed in a compressed state, and there is a gap between the compression spring 5 and one end edge of the window 11 formed in the plate portion 1b of the hub 1 due to the dimensional difference from the clearance 〓G 2 . There is also a large play area ( G3 ). G4 is a distance for allowing the stroke of the pin 13 connecting the drive plates 2, 2'.
また第１の摩擦減衰手段たる低摩擦部材１６に
は摩擦係数の小さいフリクシヨンワツシヤが使用
されていて、該低摩擦部材１６はサブプレート１
４の回動に伴つて回動し、ハブ１のプレート部１
ｂとの間で低摩擦を発生させるようになつている
と共に第２の摩擦減衰手段たる高摩擦部材１７に
は前記低摩擦部材１６よりも摩擦係数の大きなフ
リクシヨンワツシヤが使用されていて、該高摩擦
部材１７はドライブプレート２，２′の回動に伴
つて回動し、サブプレート１４との間で高摩擦を
発生させるようになつている。なお２０，２１は
第２、第３段階で作用する圧縮ばね４，５をそれ
ぞれ収容するためサブプレート１４に形成された
窓であり、第２段階で作用する圧縮ばね４を収容
する窓２０は前記ドライブプレート２，２′に設
けた窓８と略同じ大きさに形成され、また第３段
階で作用する圧縮ばね５を収容する窓２１は前記
ハブ１のプレート部１ｂに設けた窓１１と略同じ
大きさに形成されている。 Further, a friction washer having a small friction coefficient is used as the low friction member 16 serving as the first friction damping means, and the low friction member 16 is used as the sub plate 1.
The plate portion 1 of the hub 1 rotates with the rotation of the hub 1.
A friction washer having a larger coefficient of friction than the low friction member 16 is used for the high friction member 17 which is designed to generate low friction between the high friction member 17 and the second friction damping means. The high friction member 17 rotates as the drive plates 2, 2' rotate, and generates high friction with the sub-plate 14. Note that 20 and 21 are windows formed in the sub-plate 14 to accommodate the compression springs 4 and 5 that act in the second and third stages, respectively, and the window 20 that accommodates the compression spring 4 that acts in the second stage is The window 21, which is formed to have approximately the same size as the window 8 provided in the drive plates 2, 2' and accommodates the compression spring 5 that acts in the third stage, is similar to the window 11 provided in the plate portion 1b of the hub 1. They are formed to approximately the same size.
次に上記構成のクラツチデイスクの作用につい
て述べる。 Next, the operation of the clutch disc having the above structure will be described.
第３図に示す一定トルクでの作動状態からトル
ク変動が生じると、ドライブプレート２，２′の
窓８とサブプレート１４の窓２０とは円周方向略
同一幅に形成されているため、これらドライブプ
レート２，２′とサブプレート１４とは圧縮ばね
４を介して略一体に回動し、第４図に示したよう
にドライブプレート２，２′、サブプレート１４、
低摩擦部材１６、高摩擦部材１７は前記ピン１８
が、ハブ１のプレート部１ｂのピン受孔１９の一
端縁に係合するまで、即ち前記遊び間〓G1ぶん
回動する。従つて第１段階で作用する圧縮ばね３
がサブプレート１４の窓６によつてL1−G1＝L4
の長さに圧縮されて第１段階のばね反力を発生さ
せると共に低摩擦部材１６とハブ１のプレート部
１ｂとの相対回動により低摩擦を発生させ、第７
図に示す第１段階（Ａ領域）の吸振減衰作用を発
生させる。このとき、ボス部１ａとサブプレート
１４のベアリング受部１４ａ内周との間に介装さ
れたベアリング１５によつてボス部１ａの外周と
ドライブプレート２，２′及びサブプレート１４
との摩擦が小さくなると共に、サブプレート１４
がベアリング受部１４ａの内周側に設けたベアリ
ング１５によつてその内周を支持された状態で回
転するため回転面の倒れが小さく、従つて各摩擦
部材を円周方向一様に付勢するため、各摩擦部材
による摩擦力が安定して得られるので低摩擦部材
１６によつて発生させるべき所望の低摩擦が精度
よく得られ、更に、サブプレート１４等の偏摩擦
が防止できる。そして、この場合に、第２、第３
段階で作用する圧縮ばね４，５もドライブプレー
ト２，２′等に伴つて回動するが、第２段階で作
用する圧縮ばね４と窓９の一端縁との間には前記
遊び間〓G1と略等しい遊び間〓G2が存在してい
るので、該第２段階で作用する圧縮ばね４はハブ
１のプレート部１ｂの窓９の一端縁に係合するだ
けで圧縮されることはない。また第３段階で作用
する圧縮ばね５と窓１１の一端縁との間には前記
遊び間〓G2より大きい遊び間〓G3が存在してい
るので、該第３段階で作用する圧縮ばね５は前記
遊び間〓G3をG5の長さに短縮するだけであつて、
これまた圧縮されることはない。更に、第４図に
示した状態からドライブプレート２，２′を回動
させると今度は第５図に示したようにこれらドラ
イブプレート２，２′によつて第２段階で作用す
る圧縮ばね４が長さL5に圧縮されて第２段階の
ばね反力を発生させると共にドライブプレート
２，２′と高摩擦部材１７との相対回動により高
摩擦を発生させ、第７図に示す第２段階（Ｂ領
域）の吸振減衰作用を発生させる。そしてこの場
合に、第３段階で作用する圧縮ばね５もドライブ
プレート２，２′に伴つて回動するが、第３段階
で作用する圧縮ばね５と窓１１の一端縁との間に
は前記遊び間〓G3からG2を差し引いた遊び間〓
G5が存在し、この遊び間〓G5は第２段階で作用
する圧縮ばね４の作動ストロークL2−L5の大き
さに設定されているので、該第３段階で作用する
圧縮ばね５は窓１１の一端縁に係合するだけで圧
縮されることはない。そし第５図に示した状態か
らドライブプレート２，２′を更に回動させると
今度は第６図に示したようにこれらドライブプレ
ート２，２′によつて第２、第３段階で作用する
圧縮ばね４，５が同時にそれぞれ長さL6，L7に
圧縮されて第３段階のばね反力を発生させると共
にドライブプレート２，２′と高摩擦部材１７と
の相対回動により高摩擦を発生させ、第７図に示
す第３段階（Ｃ領域）の吸振減衰作用を発生させ
るのである。なお、ピン１３とハブのプレート部
１ｂに設けられた間〓G4は、各段階の圧縮ばね
が圧縮されるのに伴つてG6，G7と小さくなり、
これがプレート部１ｂに当接してストツパーとな
り第３段階の圧縮を終了する。 When torque fluctuation occurs from the constant torque operating state shown in FIG. The drive plates 2, 2' and the sub-plate 14 rotate substantially integrally via the compression spring 4, and as shown in FIG.
The low friction member 16 and the high friction member 17 are connected to the pin 18
is rotated by the amount of play G1 until it engages with one end edge of the pin receiving hole 19 of the plate portion 1b of the hub 1. Therefore, the compression spring 3 acting in the first stage
However, due to the window 6 of the sub-plate 14, L 1 −G 1 =L 4
The length of the seventh spring is compressed to generate a first-stage spring reaction force, and the relative rotation of the low-friction member 16 and the plate portion 1b of the hub 1 generates low friction.
The vibration absorption and damping effect of the first stage (area A) shown in the figure is generated. At this time, the bearing 15 interposed between the boss portion 1a and the inner circumference of the bearing receiving portion 14a of the sub-plate 14 allows the outer circumference of the boss portion 1a to
As the friction with the sub-plate 14 becomes smaller,
rotates with its inner periphery supported by the bearing 15 provided on the inner periphery side of the bearing receiving portion 14a, so the tilting of the rotating surface is small, and each friction member is biased uniformly in the circumferential direction. Therefore, since the friction force by each friction member is stably obtained, the desired low friction that should be generated by the low friction member 16 can be obtained with high accuracy, and furthermore, uneven friction of the sub-plate 14 etc. can be prevented. In this case, the second and third
The compression springs 4, 5 that act in the second stage also rotate with the drive plates 2, 2', etc., but there is the play between the compression spring 4, which acts in the second stage, and one end edge of the window 9. Since there is a play distance G 2 that is approximately equal to 1 , the compression spring 4 acting in the second stage is not compressed just by engaging with one end edge of the window 9 of the plate portion 1b of the hub 1. do not have. Furthermore, since there is a play G 3 larger than the play G 2 between the compression spring 5 that acts in the third stage and one end edge of the window 11, the compression spring 5 that acts in the third stage 5 merely shortens the play interval 〓G3 to the length of G5 , and
It is also not compressed. Further, when the drive plates 2, 2' are rotated from the state shown in FIG. 4, the compression springs 4 acting in the second stage by these drive plates 2, 2' are activated as shown in FIG. is compressed to length L 5 to generate a second stage spring reaction force, and high friction is generated by the relative rotation between the drive plates 2, 2' and the high friction member 17, and the second stage shown in FIG. A stage (B area) vibration absorption and damping effect is generated. In this case, the compression spring 5 that acts in the third stage also rotates together with the drive plates 2, 2', but there is a gap between the compression spring 5 that acts in the third stage and one end edge of the window 11. Play time = Play time obtained by subtracting G 2 from G 3
G 5 exists, and this play G 5 is set to the magnitude of the operating stroke L 2 - L 5 of the compression spring 4 that acts in the second stage, so the compression spring 5 that acts in the third stage is only engaged with one end edge of the window 11 and is not compressed. When the drive plates 2, 2' are further rotated from the state shown in Fig. 5, the drive plates 2, 2' act in the second and third stages as shown in Fig. 6. The compression springs 4 and 5 are simultaneously compressed to lengths L 6 and L 7 , respectively, to generate a third stage of spring reaction force, and the relative rotation between the drive plates 2 and 2' and the high friction member 17 generates high friction. This causes the vibration absorption and damping action of the third stage (region C) shown in FIG. 7 to occur. Note that the distance G 4 between the pin 13 and the plate portion 1b of the hub decreases to G 6 and G 7 as the compression springs at each stage are compressed.
This contacts the plate portion 1b and becomes a stopper, completing the third stage of compression.
従つて、第１段階で作用する圧縮ばね３はサブ
プレート１４がハブ１のプレート部１ａに係合す
るまで圧縮され、サブプレート１４がハブ１のプ
レート部１ａに係合して以降は圧縮されることが
ないので、この第１段階で作用する圧縮ばね３の
応力は大きくなることはない。また、第１段階で
作用する圧縮ばね３の配置スペースが小さいか
ら、その分第２段階以降で作用する圧縮ばねの配
置スペースを大きくして捩じり角度を増大させる
ことができる。 Therefore, the compression spring 3 acting in the first stage is compressed until the sub-plate 14 engages with the plate portion 1a of the hub 1, and is not compressed after the sub-plate 14 engages with the plate portion 1a of the hub 1. Therefore, the stress of the compression spring 3 that acts in this first stage does not become large. Further, since the space for arranging the compression spring 3 that acts in the first stage is small, the space for arranging the compression spring 3 that acts in the second and subsequent stages can be enlarged to increase the torsion angle.
発明の効果
以上詳細に説明したように、この発明によれ
ば、ボス部とプレート部とを有するハブと、この
ハブに対して相対回動可能に連繋されたドライブ
プレートと、前記ハブのプレート部とドライブプ
レートとの間に設けられ、摩擦減衰手段の作用制
御を司るサブプレートと、このサブプレートと前
記ハブプレート部との間に介装された第１の摩擦
減衰手段と、前記サブプレートとドライブプレー
トとの間に介装された第２の摩擦減衰手段とを備
えたクラツチデイスクにおいて、前記第１の摩擦
減衰手段の摩擦力を前記第２の摩擦減衰手段の摩
擦力よりも小さくすると共に、前記サブプレート
の内周部に、ハブのボス部の外周に沿つて筒状の
ベアリング受部を形成し、このサブプレートを前
記受部の内周側に設けたベアリングを介してハブ
のボス部外周に取り付けたことにより、サブプレ
ートはハブとの間で摩耗等を生ずること無く滑ら
かに回転し、摩擦減衰手段による所期する減衰能
を安定して得ることができる。Effects of the Invention As described in detail above, according to the present invention, there is provided a hub having a boss portion and a plate portion, a drive plate coupled to the hub so as to be rotatable relative to the hub, and a plate portion of the hub. a sub-plate provided between the drive plate and the drive plate and controlling the operation of the friction damping means; a first friction damping means interposed between the sub-plate and the hub plate portion; and a second friction damping means interposed between the clutch disk and the drive plate, wherein the friction force of the first friction damping means is made smaller than the friction force of the second friction damping means. , a cylindrical bearing receiving part is formed on the inner peripheral part of the sub-plate along the outer periphery of the boss part of the hub, and this sub-plate is connected to the hub boss of the hub via a bearing provided on the inner peripheral side of the receiving part. By being attached to the outer periphery of the sub-plate, the sub-plate rotates smoothly without causing wear etc. with the hub, and the desired damping ability by the friction damping means can be stably obtained.
またベアリングで発生した摩耗粉はベアリング
受部によつて第２の摩擦減衰手段側に侵入するの
を防止し、前記摩耗粉が第２の摩擦減衰手段の性
能に悪影響を及ぼすのを防止することができる。 Further, the abrasion powder generated in the bearing is prevented from entering the second friction damping means side by the bearing receiving part, and the abrasion powder is prevented from having an adverse effect on the performance of the second friction damping means. I can do it.
また第１の摩擦減衰手段と、第２の摩擦減衰手
段との間にサブプレートを配置し、このサブプレ
ートにベアリング受部を形成したことにより、サ
ブプレートで第１、第２の摩擦減衰手段の間を隔
成し、これら第１または第２の摩擦減衰手段から
発生する摩耗粉が他方の摩擦減衰手段の性能に悪
影響を及ぼすのを防止して、所期する安定した減
衰能を得ることができる。 Furthermore, by arranging a sub-plate between the first friction damping means and the second friction damping means and forming a bearing receiving part on this sub-plate, the sub-plate can be used as the first and second friction damping means. To prevent wear particles generated from the first or second friction damping means from adversely affecting the performance of the other friction damping means, thereby obtaining the desired stable damping performance. I can do it.
第１図は本発明のクラツチデイスクの平面図、
第２図は第１図の−線断面図、第３図は非作
動状態におけるクラツチデイスクの展開断面図、
第４図は第１段階で作用する圧縮ばねを圧縮した
状態の展開断面図、第５図は第２段階で作用する
圧縮ばねを圧縮した状態の展開断面図、第６図は
第３段階で作用する圧縮ばねを圧縮した状態の展
開断面図、第７図は特性図である。
１……ハブ、１ａ……ボス部、１ｂ……プレー
ト部、２，２′……ドライブプレート、３，４，
５……圧縮ばね、６，７，８，９，１０，１１…
…窓、１４……サブプレート、１５……ベアリン
グ、１６……第１の摩擦減衰手段（低摩擦部材）、
１７……第２の摩擦減衰手段（高摩擦部材）、２
０，２０……窓。
FIG. 1 is a plan view of the clutch disk of the present invention;
FIG. 2 is a sectional view taken along the - line in FIG.
Figure 4 is a developed cross-sectional view of the compression spring acting in the first stage in a compressed state, Figure 5 is a developed cross-sectional view of the compression spring acting in the second stage in a compressed state, and Figure 6 is a developed cross-sectional view of the compressed state in which the compression spring acts in the second stage. FIG. 7 is a developed cross-sectional view of the acting compression spring in a compressed state, and is a characteristic diagram. 1...Hub, 1a...Boss part, 1b...Plate part, 2, 2'...Drive plate, 3, 4,
5... Compression spring, 6, 7, 8, 9, 10, 11...
... window, 14 ... subplate, 15 ... bearing, 16 ... first friction damping means (low friction member),
17...Second friction damping means (high friction member), 2
0,20...window.
Claims (1)
ハブに対して相対回動可能に連繋されたドライブ
プレートと、前記ハブのプレート部とドライブプ
レートとの間に設けられ、摩擦減衰手段の作用制
御を司るサブプレートと、このサブプレートと前
記ハブプレート部との間に介装された第１の摩擦
減衰手段と、前記サブプレートとドライブプレー
トとの間に介装された第２の摩擦減衰手段とを備
えたクラツチデイスクにおいて、前記第１の摩擦
減衰手段の摩擦力を前記第２の摩擦減衰手段の摩
擦力よりも小さくすると共に、前記サブプレート
の内周部に、ハブのボス部の外周に沿つて筒状の
ベアリング受部を形成し、このサブプレートを前
記受部の内周側に設けたベアリングを介してハブ
のボス部外周に取付けたことを特徴とするクラツ
チデイスク。1. A hub having a boss portion and a plate portion, a drive plate connected to the hub so as to be rotatable relative to the hub, and a friction damping means provided between the plate portion of the hub and the drive plate, and controlling the operation of a friction damping means. a first friction damping means interposed between the sub plate and the hub plate portion, and a second friction damping means interposed between the sub plate and the drive plate. In the clutch disk, the friction force of the first friction damping means is made smaller than the friction force of the second friction damping means, and an outer periphery of the boss portion of the hub is provided on the inner periphery of the sub-plate. 1. A clutch disk characterized in that a cylindrical bearing receiving part is formed along the bearing part, and this sub-plate is attached to the outer periphery of a boss part of a hub via a bearing provided on the inner peripheral side of the receiving part.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1429183A JPS59140923A (en) | 1983-01-31 | 1983-01-31 | Clutch disc |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1429183A JPS59140923A (en) | 1983-01-31 | 1983-01-31 | Clutch disc |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59140923A JPS59140923A (en) | 1984-08-13 |
| JPH0368245B2 true JPH0368245B2 (en) | 1991-10-25 |
Family
ID=11856983
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1429183A Granted JPS59140923A (en) | 1983-01-31 | 1983-01-31 | Clutch disc |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59140923A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6163019U (en) * | 1984-09-29 | 1986-04-28 | ||
| DE8525579U1 (en) * | 1985-09-07 | 1993-06-03 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Device for compensating torsional shocks |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50107630A (en) * | 1974-01-31 | 1975-08-25 | ||
| JPS5417110A (en) * | 1977-06-02 | 1979-02-08 | Mosbach Klaus H | Production of magnetic polymer particle supporting drug |
| JPS5757924A (en) * | 1980-09-25 | 1982-04-07 | Daikin Mfg Co Ltd | Damper disc |
| JPS57134019A (en) * | 1981-02-13 | 1982-08-19 | Daikin Mfg Co Ltd | Clutch disc |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU532122B2 (en) * | 1979-06-07 | 1983-09-15 | Automotive Products Ltd. | Friction clutch driven plate |
-
1983
- 1983-01-31 JP JP1429183A patent/JPS59140923A/en active Granted
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50107630A (en) * | 1974-01-31 | 1975-08-25 | ||
| JPS5417110A (en) * | 1977-06-02 | 1979-02-08 | Mosbach Klaus H | Production of magnetic polymer particle supporting drug |
| JPS5757924A (en) * | 1980-09-25 | 1982-04-07 | Daikin Mfg Co Ltd | Damper disc |
| JPS57134019A (en) * | 1981-02-13 | 1982-08-19 | Daikin Mfg Co Ltd | Clutch disc |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59140923A (en) | 1984-08-13 |
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