JPH094680A - Friction generating mechanism - Google Patents
Friction generating mechanismInfo
- Publication number
- JPH094680A JPH094680A JP7156246A JP15624695A JPH094680A JP H094680 A JPH094680 A JP H094680A JP 7156246 A JP7156246 A JP 7156246A JP 15624695 A JP15624695 A JP 15624695A JP H094680 A JPH094680 A JP H094680A
- Authority
- JP
- Japan
- Prior art keywords
- friction
- plate member
- side plate
- plate
- annular
- 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.)
- Granted
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
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/68—Attachments of plates or lamellae to their supports
- F16D13/686—Attachments of plates or lamellae to their supports with one or more intermediate members made of rubber or like material transmitting torque from the linings to the hub
-
- 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
-
- 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
-
- 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
- F16D2013/642—Clutch-plates; Clutch-lamellae with resilient attachment of frictions rings or linings to their supporting discs or plates for allowing limited axial displacement of these rings or linings
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)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、摩擦発生機構、特に、
トルク伝達時における捩じり振動を減衰するための摩擦
発生機構に関する。BACKGROUND OF THE INVENTION The present invention relates to a friction generating mechanism, and more particularly to a friction generating mechanism.
The present invention relates to a friction generating mechanism for damping torsional vibration during torque transmission.
【０００２】[0002]
【従来の技術】車輌のクラッチ装置に用いられるクラッ
チディスク組立体は、主に、入力側部材としてのクラッ
チプレート及びリテーニングプレートと、フランジを有
しトランスミッション側から延びるシャフトに連結され
るハブと、クラッチプレート及びリテーニングプレート
とフランジとの間で両者が相対回転すると円周方向に圧
縮されるように配置されたコイルスプリングと、両プレ
ートとフランジとが相対回転するときに摩擦を発生させ
る摩擦発生機構とを備えている。さらに、両プレートの
外周側には摩擦フェーシングが固定されており、この摩
擦フェーシングがプレッシャプレートによりフライホイ
ールに押圧されると、フライホイールからクラッチディ
スク組立体にトルクが入力される。2. Description of the Related Art A clutch disc assembly used in a vehicle clutch device mainly comprises a clutch plate and a retaining plate as input members, a hub having a flange and connected to a shaft extending from the transmission side, A friction spring that generates friction when the coil plate and the flange are rotated relative to each other and the coil spring that is arranged so as to be compressed in the circumferential direction when they rotate relative to each other between the clutch plate and the retaining plate. And a mechanism. Further, friction facings are fixed to the outer peripheral sides of both plates, and when the friction facings are pressed against the flywheel by the pressure plate, torque is input from the flywheel to the clutch disc assembly.
【０００３】従来の摩擦発生機構は、たとえば、フラン
ジに当接する摩擦部材と、摩擦部材の側方に配置されリ
テーニングプレートと一体回転するように係合するプレ
ート部材と、プレート部材をフランジ側に付勢する付勢
部材とから構成されている。A conventional friction generating mechanism includes, for example, a friction member that abuts a flange, a plate member that is disposed on the side of the friction member and that engages so as to rotate integrally with a retaining plate, and a plate member that faces the flange. And a biasing member for biasing.
【０００４】[0004]
【発明が解決しようとする課題】前記従来の摩擦発生機
構では、摩擦が発生するのは摩擦部材とフランジとの間
の１面だけである。したがって、ここで生じる摩擦の大
きさには限界があり、大きな摩擦を必要とする場合に対
応できない。本発明の目的は、摩擦発生機構において大
きな摩擦を発生させることにある。In the conventional friction generating mechanism, friction is generated only on one surface between the friction member and the flange. Therefore, there is a limit to the magnitude of the friction generated here, and it is not possible to deal with the case where a large friction is required. An object of the present invention is to generate large friction in the friction generating mechanism.
【０００５】[0005]
【課題を解決するための手段】請求項１に記載の摩擦発
生機構は、入力側プレート部材と出力側プレート部材と
環状摩擦部材と第１プレート部材と第２プレート部材と
付勢部材とを備えている。出力側プレート部材は、入力
側プレート部材の側方に相対回転自在に配置されてい
る。複数の摩擦部材は、両プレート部材間に入力側プレ
ート部材側から順番に配置された第１環状摩擦部材、第
２環状摩擦部材及び第３環状摩擦部材を含んでいる。第
１プレート部材は、第２環状摩擦部材と第３環状摩擦部
材との間に挟まれた第１環状部を有し、入力側プレート
部材に回転方向に連結されている。第２プレート部材
は、第１環状摩擦部材と第２環状摩擦部材との間に挟ま
れた第２環状部を有し、出力側プレート部材に回転方向
に連結されている。付勢部材は、入力側プレート部材と
出力側プレート部材とを互いに接近する方向に付勢す
る。A friction generating mechanism according to claim 1 comprises an input side plate member, an output side plate member, an annular friction member, a first plate member, a second plate member and a biasing member. ing. The output side plate member is disposed relatively laterally to the input side plate member. The plurality of friction members include a first annular friction member, a second annular friction member, and a third annular friction member that are arranged between the plate members in order from the input side plate member side. The first plate member has a first annular portion sandwiched between a second annular friction member and a third annular friction member, and is rotationally connected to the input side plate member. The second plate member has a second annular portion sandwiched between the first annular friction member and the second annular friction member, and is rotationally connected to the output side plate member. The urging member urges the input-side plate member and the output-side plate member toward each other.
【０００６】請求項２に記載の摩擦発生機構では、第１
プレート部材と第２プレート部材はそれぞれ入力側プレ
ート部材と出力側プレート部材に対して相対回転不能に
かつ軸方向に移動可能に連結されている。請求項３に記
載の摩擦発生機構では、第１プレート部材は入力側プレ
ート部材に軸方向に移動可能にかつ所定角度間で相対回
転可能に連結されている。According to a second aspect of the friction generating mechanism,
The plate member and the second plate member are connected to the input side plate member and the output side plate member, respectively, such that they cannot rotate relative to each other and are movable in the axial direction. In the friction generating mechanism according to the third aspect, the first plate member is coupled to the input side plate member so as to be movable in the axial direction and relatively rotatable within a predetermined angle.
【０００７】請求項４に記載の摩擦発生機構では、第２
プレート部材は出力側プレート部材に軸方向に移動可能
にかつ所定角度間で相対回転可能に連結されている。請
求項５に記載の摩擦発生機構では、第１プレート部材
は、第１環状部と、第１環状部から軸方向に延び入力側
プレート部材に連結される複数の第１連結部とを有し、
第２プレート部材は、第２環状部と第２環状部から軸方
向に延び出力側プレート部材に連結される複数の第２連
結部とを有している。In the friction generating mechanism according to claim 4, the second
The plate member is connected to the output side plate member so as to be movable in the axial direction and relatively rotatable at a predetermined angle. In the friction generating mechanism according to claim 5, the first plate member has a first annular portion and a plurality of first connecting portions extending in the axial direction from the first annular portion and connected to the input side plate member. ,
The second plate member has a second annular portion and a plurality of second connecting portions extending in the axial direction from the second annular portion and connected to the output side plate member.
【０００８】[0008]
【作用】請求項１に記載の摩擦発生機構では、たとえば
捩じり振動が入力されて入力側プレート部材が出力側プ
レート部材に対して相対回転したとする。すると、入力
側プレート部材と第２プレート部材との間で第１環状摩
擦部材が円周方向に摺動し、第１プレート部材の第１環
状部と第２プレート部材の第２環状部との間で第２環状
摩擦部材が円周方向に摺動し、第１プレート部材の第１
環状部と出力側プレート部材との間で第３環状摩擦部材
が円周方向に摺動する。ここでは、摩擦面が３面である
ために大きな摩擦が発生する。In the friction generating mechanism according to the first aspect of the present invention, it is assumed that, for example, torsional vibration is input and the input side plate member rotates relative to the output side plate member. Then, the first annular friction member slides in the circumferential direction between the input side plate member and the second plate member, and the first annular portion of the first plate member and the second annular portion of the second plate member are separated from each other. The second annular friction member slides in the circumferential direction between the first plate member and the first plate member.
The third annular friction member slides in the circumferential direction between the annular portion and the output side plate member. Here, since there are three friction surfaces, large friction occurs.
【０００９】請求項２に記載の摩擦発生機構では、第１
プレート部材と第２プレート部材とはそれぞれ入力側プ
レート部材と出力側プレート部材に相対回転不能に連結
されているため、入力側プレート部材と出力側プレート
部材との相対角度の大きさが変化しても発生する摩擦の
大きさは一定である。請求項３に記載の摩擦発生機構で
は、入力側プレート部材と出力側プレート部材との相対
捩じり角度が小さな範囲では、第１プレート部材は、第
２プレート部材、第２環状摩擦部材及び第３環状摩擦部
材とともに出力側プレート部材と一体回転する。すなわ
ち、ここでは入力側プレート部材と第２プレート部材と
の間で第１環状摩擦部材のみが円周方向に摺動する。こ
のように摩擦面は１面なので小さな摩擦が発生する。捩
じり角度が大きくなって第１プレート部材が入力側プレ
ート部材と一体回転するようになると、摩擦面が３面に
なり大きな摩擦が得られる。According to another aspect of the friction generating mechanism of the present invention,
Since the plate member and the second plate member are connected to the input side plate member and the output side plate member, respectively, so that they cannot rotate relative to each other, the magnitude of the relative angle between the input side plate member and the output side plate member changes. Also, the amount of friction generated is constant. In the friction generating mechanism according to claim 3, the first plate member is the second plate member, the second annular friction member, and the second annular friction member within a range in which the relative twist angle between the input side plate member and the output side plate member is small. 3 Rotates integrally with the output plate member together with the annular friction member. That is, here, only the first annular friction member slides in the circumferential direction between the input side plate member and the second plate member. Thus, since there is only one friction surface, a small amount of friction occurs. When the twisting angle becomes large and the first plate member rotates integrally with the input side plate member, the friction surface becomes three surfaces and a large friction is obtained.
【００１０】請求項４に記載の摩擦発生機構では、入力
側プレート部材と出力側プレート部材との相対捩じり角
度が小さな範囲では、第２プレート部材は、第１プレー
ト部材、第１環状摩擦部材及び第２環状摩擦部材ととも
に入力側プレート部材と一体回転する。すなわち、ここ
では出力側プレート部材と第１プレート部材との間で第
３環状摩擦部材のみが円周方向に摺動する。このように
摩擦面は１面なので小さな摩擦が発生する。捩じり角度
が大きくなって第２プレート部材が出力側プレート部材
と一体回転するようになると、摩擦面が３面になり大き
な摩擦が得られる。According to another aspect of the friction generating mechanism of the present invention, the second plate member is the first plate member and the first annular friction member within a range where the relative twist angle between the input side plate member and the output side plate member is small. The member and the second annular friction member rotate integrally with the input side plate member. That is, here, only the third annular friction member slides in the circumferential direction between the output side plate member and the first plate member. Thus, since there is only one friction surface, a small amount of friction occurs. When the twisting angle becomes large and the second plate member rotates integrally with the output side plate member, the friction surface becomes three surfaces and a large friction is obtained.
【００１１】請求項５に記載の摩擦発生機構では、各プ
レート部材は環状部と複数の連結部とを有している。こ
のように簡単な構造のプレート部材を複数の摩擦部材に
組み合わせることで前述したように大きな摩擦を得るこ
とができる。In the friction generating mechanism according to the fifth aspect, each plate member has an annular portion and a plurality of connecting portions. By combining the plate member having such a simple structure with a plurality of friction members, a large friction can be obtained as described above.
【００１２】[0012]
【実施例】第１実施例 図１に示すクラッチディスク組立体１は、入力側部材と
してのクラッチプレート３及びリテーニングプレート４
と、フランジ５を有する出力側部材としてのハブ６と、
両プレート３，４とフランジ５との間で配置された複数
のコイルスプリング７と、摩擦発生機構８と、摩擦連結
部９とから構成されている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment A clutch disc assembly 1 shown in FIG. 1 includes a clutch plate 3 and a retaining plate 4 as input side members.
And a hub 6 as an output side member having a flange 5,
It is composed of a plurality of coil springs 7 arranged between the plates 3 and 4 and the flange 5, a friction generating mechanism 8 and a friction connecting portion 9.
【００１３】クラッチプレート３及びリテーニングプレ
ート４は概ね円板状のプレート部材である。両プレート
３，４はともに中心孔を有しており、ハブ６の外周に回
転自在に嵌合している。プレート３，４は外周側で複数
のストップピン（図示せず）により互いに固定されてい
る。ハブ６には、トランスミッション側から延びるシャ
フト（図示せず）と係合するスプライン孔６ａが中心に
形成されている。また、フランジ５はプレート３，４間
で径方向外方に延びており、円周方向に並んだ複数の窓
孔５ａを有している。この窓孔５ａ内には、それぞれコ
イルスプリング７が配置されている。プレート３，４に
おいて窓孔５ａに対応する部分には切起し部３ａ，４ａ
が形成されている。この切起し部３ａ，４ａによりコイ
ルスプリング７は径方向外方及び軸方向へ移動が抑えら
れている。The clutch plate 3 and the retaining plate 4 are plate members having a substantially disc shape. Both plates 3 and 4 have a central hole, and are rotatably fitted to the outer periphery of the hub 6. The plates 3 and 4 are fixed to each other on the outer peripheral side by a plurality of stop pins (not shown). A spline hole 6a that engages with a shaft (not shown) extending from the transmission side is formed at the center of the hub 6. The flange 5 extends radially outward between the plates 3 and 4 and has a plurality of window holes 5a arranged in the circumferential direction. Coil springs 7 are arranged in the window holes 5a, respectively. Cut-and-raised portions 3a and 4a are formed in portions of the plates 3 and 4 corresponding to the window holes 5a.
Are formed. The cut-and-raised portions 3a and 4a prevent the coil spring 7 from moving radially outward and axially.
【００１４】摩擦連結部９は、複数のクッショニングプ
レート１１と、クッショニングプレート１１の両面に固
定された摩擦フェーシング１２とから構成されている。
各クッショニングプレート１１はリベット１０によりク
ラッチプレート３の外周に連結されている。摩擦連結部
９の図１左側には図示しないフライホイールが配置され
ており、摩擦連結部９がフライホイール側に押圧される
とフライホイールと摩擦連結部９が摩擦により連結さ
れ、フライホイールからクラッチディスク組立体１にト
ルクが入力される。The friction connecting portion 9 is composed of a plurality of cushioning plates 11 and friction facings 12 fixed to both surfaces of the cushioning plates 11.
Each cushioning plate 11 is connected to the outer periphery of the clutch plate 3 by a rivet 10. A flywheel (not shown) is arranged on the left side of the friction connecting portion 9 in FIG. Torque is input to the disc assembly 1.
【００１５】次に、図２〜４を用いて摩擦発生機構８に
ついて説明する。摩擦発生機構８は、第１摩擦部材１４
と第２摩擦部材１５と第３摩擦部材１６と第１プレート
１７と第２プレート１８とコーンスプリング１９とから
構成される。第１摩擦部材１４、第２摩擦部材１５及び
第３摩擦部材１６は、ワッシャ形状である。第１摩擦部
材１４、第２摩擦部材１５及び第３摩擦部材１６は、こ
の順でクラッチプレート３の内周端とフランジ５の内周
部との間にクラッチプレート３側から順番に配置されて
いる。Next, the friction generating mechanism 8 will be described with reference to FIGS. The friction generating mechanism 8 includes the first friction member 14
And a second friction member 15, a third friction member 16, a first plate 17, a second plate 18, and a cone spring 19. The first friction member 14, the second friction member 15, and the third friction member 16 have a washer shape. The first friction member 14, the second friction member 15, and the third friction member 16 are arranged in this order between the inner peripheral end of the clutch plate 3 and the inner peripheral portion of the flange 5 from the clutch plate 3 side. There is.
【００１６】第１プレート１７は、図４に示すように、
環状の環状部１７ａと、環状部１７ａの外周縁からクラ
ッチプレート３側に延びる４つの係合部１７ｂとを有し
ている。環状部１７ａは第２摩擦部材１５と第３摩擦部
材１６との間に配置されている。４つの係合部１７ｂは
円周方向に等間隔で設けられている。係合部１７ｂはク
ラッチプレート３の内周部に形成された４つの切欠き溝
３ｂ内に挿入されている。この係合により、第１プレー
ト１７はクラッチプレート３に対して円周方向に相対回
転不能にかつ軸方向に移動自在となっている。The first plate 17 is, as shown in FIG.
It has an annular portion 17a and four engaging portions 17b extending from the outer peripheral edge of the annular portion 17a toward the clutch plate 3 side. The annular portion 17 a is arranged between the second friction member 15 and the third friction member 16. The four engaging portions 17b are provided at equal intervals in the circumferential direction. The engaging portion 17b is inserted into four notch grooves 3b formed in the inner peripheral portion of the clutch plate 3. Due to this engagement, the first plate 17 cannot rotate relative to the clutch plate 3 in the circumferential direction and can move in the axial direction.
【００１７】第２プレート１８は、第１プレート１７と
同じく環状部１８ａと４つの係合部１８ｂとを有してい
る。環状部１８ａは、第１摩擦部材１４と第２摩擦部材
１５との間に配置されている。第２プレート１８の係合
部１８ｂは、フランジ５の内周部に形成された各切欠き
溝５ｂ内に挿入されている。これにより、第２プレート
１８はフランジ５に対して円周方向に相対回転不能にか
つ軸方向に移動自在に係合している。切欠き溝５ｂ及び
係合部１８ｂは、切欠き溝３ｂ及び係合部１７ｂに対し
て、円周方向に交互に等間隔で配置されている。The second plate 18 has an annular portion 18a and four engaging portions 18b, like the first plate 17. The annular portion 18 a is arranged between the first friction member 14 and the second friction member 15. The engaging portion 18b of the second plate 18 is inserted into each notch groove 5b formed in the inner peripheral portion of the flange 5. As a result, the second plate 18 is engaged with the flange 5 such that the second plate 18 cannot rotate in the circumferential direction and can move in the axial direction. The cutout grooves 5b and the engaging portions 18b are alternately arranged at equal intervals in the circumferential direction with respect to the cutout grooves 3b and the engaging portions 17b.
【００１８】フランジ５の内周部とリテーニングプレー
ト４の内周部との間にはコーンスプリング１９が配置さ
れている。コーンスプリング１９は圧縮されており、外
周部がフランジ５をクラッチプレート３側に付勢し、内
周部がリテーニングプレート４をフランジ５から離れる
方向に付勢している。これにより、リテーニングプレー
ト４に固定されたクラッチプレート３はフランジ５に接
近する方向に付勢されている。この結果、摩擦発生機構
８を構成する各部材が軸方向に互いに圧接される。A cone spring 19 is arranged between the inner peripheral portion of the flange 5 and the inner peripheral portion of the retaining plate 4. The cone spring 19 is compressed, and the outer peripheral portion urges the flange 5 toward the clutch plate 3 side, and the inner peripheral portion urges the retaining plate 4 away from the flange 5. As a result, the clutch plate 3 fixed to the retaining plate 4 is biased toward the flange 5. As a result, the members forming the friction generating mechanism 8 are pressed against each other in the axial direction.
【００１９】摩擦連結部９が図示しないフライホイール
に押圧されると、フライホイールからクラッチディスク
組立体１にトルクが入力される。このトルクは、プレー
ト３，４、コイルスプリング７、フランジ５及びハブ６
を介してトランスミッション側から延びるシャフト（図
示せず）に出力される。フライホイール側から捩じり振
動がクラッチディスク組立体１に入力されると、プレー
ト４とフランジ５とが相対回転する。このときコイルス
プリング７は伸縮を繰り返す。そして、摩擦発生機構８
で発生する摩擦により捩じり振動が減衰される。When the friction coupling portion 9 is pressed by a flywheel (not shown), torque is input to the clutch disc assembly 1 from the flywheel. This torque is applied to the plates 3 and 4, the coil spring 7, the flange 5 and the hub 6.
Is output to a shaft (not shown) extending from the transmission side via. When torsional vibration is input to the clutch disc assembly 1 from the flywheel side, the plate 4 and the flange 5 rotate relative to each other. At this time, the coil spring 7 repeats expansion and contraction. Then, the friction generating mechanism 8
The torsional vibration is damped by the friction generated at.
【００２０】摩擦発生機構８では、クラッチプレート３
がフランジ５に対して相対回転すると、クラッチプレー
ト３と第１プレート１７の環状部１７ａとの間で第１摩
擦部材１４が摺動し、環状部１７ａと第２プレート１８
の環状部１８ａとの間で第２摩擦部材１５が摺動し、環
状部１８ａとフランジ５との間で第３摩擦部材１６が摺
動する。このように摩擦面が３面であり従来より多くな
っているために、大きな摩擦が得られる。ここでは、３
枚の摩擦部材と２枚のプレートからなる簡単な構造で大
きな摩擦が得られる。第２実施例 前記実施例では、クラッチプレート３と第２プレート１
８は相対回転不能であり、フランジ５と第１プレート１
７は相対回転不能であるが、これら同士を所定角度まで
は相対回転可能にしてもよい。図５におけるクラッチプ
レート３には、円周方向に長く延びる切欠き溝３ｂが形
成されている。このため、第２プレート１８の係合部１
８ｂは所定角度内でクラッチプレート３に相対回転可能
になっている。この場合、捩じり角度の小さな範囲では
第２プレート１８は第１プレート１７、第２摩擦部材１
５及び第３摩擦部材１６とともに回転する。すなわち、
このときはクラッチプレート３と第１プレート１７の環
状部１７ａとの間で第１摩擦部材が摺動するだけで摩擦
面は１面である。したがって発生する摩擦は小さい。捩
じり角度が大きくなって第２プレート１８の係合部１８
ｂがクラッチプレート３の切欠き溝３ｂの円周方向端部
に当接すると、以後は前記実施例で述べたように３面の
摩擦面による大きな摩擦が得られる。このようにして小
さな摩擦と大きな摩擦とが捩じり角度の変化に応じて得
られる。In the friction generating mechanism 8, the clutch plate 3
Is rotated relative to the flange 5, the first friction member 14 slides between the clutch plate 3 and the annular portion 17a of the first plate 17, and the annular portion 17a and the second plate 18 are slid.
The second friction member 15 slides between the annular portion 18a and the annular portion 18a, and the third friction member 16 slides between the annular portion 18a and the flange 5. As described above, the friction surface is three, which is larger than that of the conventional one, so that a large friction can be obtained. Here, 3
Large friction can be obtained with a simple structure consisting of one friction member and two plates. Second Embodiment In the above embodiment, the clutch plate 3 and the second plate 1 are used.
8 is non-rotatable relative to the flange 5 and the first plate 1
Although 7 cannot rotate relative to each other, they may rotate relative to each other up to a predetermined angle. The clutch plate 3 in FIG. 5 is formed with a notch groove 3b that extends in the circumferential direction. Therefore, the engaging portion 1 of the second plate 18
8b is rotatable relative to the clutch plate 3 within a predetermined angle. In this case, in the range where the twist angle is small, the second plate 18 is the first plate 17 and the second friction member 1
5 and the third friction member 16 rotate together. That is,
At this time, the first friction member simply slides between the clutch plate 3 and the annular portion 17a of the first plate 17, and the friction surface is one. Therefore, the generated friction is small. The twisting angle increases, and the engaging portion 18 of the second plate 18
When b comes into contact with the circumferential end of the cutout groove 3b of the clutch plate 3, a large amount of friction is obtained by the three friction surfaces, as described in the above embodiment. In this way, a small friction and a large friction are obtained according to the change of the twist angle.
【００２１】フランジ５の係合凹部５ｂを円周方向に延
ばせば、同様の効果が得られる。さらに、両方の切欠き
溝３ｂ，５ｂを円周方向に延ばせば、摩擦発生機構８で
摩擦が発生しない領域が得られる。さらに、クラッチプ
レート３とフランジ５における切欠き溝３ｂ，５ｂの円
周方向の長さまたは係合部１７ｂ，１８ｂの円周方向長
さを調整すれば摩擦の大きさの変更タイミングを様々に
設定できる。The same effect can be obtained by extending the engagement recess 5b of the flange 5 in the circumferential direction. Further, if both the notched grooves 3b and 5b are extended in the circumferential direction, a region where friction does not occur in the friction generating mechanism 8 can be obtained. Further, by adjusting the circumferential lengths of the cutout grooves 3b and 5b in the clutch plate 3 and the flange 5 or the circumferential lengths of the engaging portions 17b and 18b, various timings for changing the magnitude of friction can be set. it can.
【００２２】[0022]
【発明の効果】本発明に係る摩擦発生機構では、捩じり
振動が入力されると、入力側プレート部材が出力側プレ
ート部材に対して相対回転する。すると、入力側プレー
ト部材と第２プレート部材との間で第１環状摩擦部材が
円周方向に摺動し、第１プレート部材の第１環状部と第
２プレート部材の第２環状部との間で第２環状摩擦部材
が円周方向に摺動し、第１プレート部材の第１環状部と
出力側プレート部材との間で第３環状摩擦部材が円周方
向に摺動する。ここでは、摩擦面が３面であるために大
きな摩擦が発生する。In the friction generating mechanism according to the present invention, when the torsional vibration is input, the input side plate member rotates relative to the output side plate member. Then, the first annular friction member slides in the circumferential direction between the input side plate member and the second plate member, and the first annular portion of the first plate member and the second annular portion of the second plate member are separated from each other. The second annular friction member slides in the circumferential direction between them, and the third annular friction member slides in the circumferential direction between the first annular portion of the first plate member and the output side plate member. Here, since there are three friction surfaces, large friction occurs.
【００２３】入力側プレート部材と出力側プレート部材
がそれぞれ第２プレート部材と第１プレート部材と所定
角度間で相対回転可能にすれば、捩じり角度の変化に応
じて摩擦の大きさを変更できる。簡単な構造のプレート
部材を複数の摩擦部材に組み合わせることで前述したよ
うに大きな摩擦を得ることができる。If the input side plate member and the output side plate member are respectively rotatable relative to the second plate member and the first plate member within a predetermined angle, the magnitude of friction is changed according to the change of the twist angle. it can. By combining a plate member having a simple structure with a plurality of friction members, large friction can be obtained as described above.
【図１】本発明の第１実施例におけるクラッチディスク
組立体の部分縦断面図。FIG. 1 is a partial vertical cross-sectional view of a clutch disc assembly according to a first embodiment of the present invention.
【図２】本発明の一実施例としての摩擦発生機構の縦断
面概略図。FIG. 2 is a schematic vertical sectional view of a friction generating mechanism as one embodiment of the present invention.
【図３】摩擦発生機構の縦断面概略図。FIG. 3 is a schematic vertical sectional view of a friction generating mechanism.
【図４】第１プレートの正面図。FIG. 4 is a front view of a first plate.
【図５】第２実施例におけるクラッチプレートと第１プ
レートとの係合状態を示す部分平面図。FIG. 5 is a partial plan view showing an engaged state of a clutch plate and a first plate in the second embodiment.
１ クラッチディスク組立体 ３ クラッチプレート ４ リテーニングプレート ５ フランジ ８ 摩擦発生機構 １４ 第１摩擦部材 １５ 第２摩擦部材 １６ 第３摩擦部材 １７ 第１プレート １８ 第２プレート DESCRIPTION OF SYMBOLS 1 Clutch disc assembly 3 Clutch plate 4 Retaining plate 5 Flange 8 Friction generating mechanism 14 First friction member 15 Second friction member 16 Third friction member 17 First plate 18 Second plate
Claims (5)
れた出力側プレート部材と、 前記プレート部材間に前記入力側プレート部材側から順
番に配置された第１環状摩擦部材、第２環状摩擦部材及
び第３環状摩擦部材を含む複数の環状摩擦部材と、 前記第２環状摩擦部材と前記第３環状摩擦部材との間に
挟まれた第１環状部を有し、前記入力側プレート部材に
回転方向に連結された第１プレート部材と、 前記第１環状摩擦部材と前記第２環状摩擦部材との間に
挟まれた第２環状部を有し、前記出力側プレート部材に
回転方向に連結された第２プレート部材と、 前記入力側プレート部材と前記出力側プレート部材とを
互いに接近する方向に付勢する付勢部材と、を備えた摩
擦発生機構。1. An input-side plate member, an output-side plate member rotatably disposed laterally of the input-side plate member, and an order of arrangement between the plate members from the input-side plate member side. A plurality of annular friction members including a first annular friction member, a second annular friction member and a third annular friction member, and a first annular portion sandwiched between the second annular friction member and the third annular friction member. A first plate member rotationally connected to the input side plate member, and a second annular portion sandwiched between the first annular friction member and the second annular friction member, A friction generating mechanism including a second plate member rotationally connected to the output side plate member, and a biasing member for biasing the input side plate member and the output side plate member in directions toward each other. .
材はそれぞれ前記入力側プレート部材と前記出力側プレ
ート部材に相対回転不能にかつ軸方向に移動可能に連結
されている、請求項１に記載の摩擦発生機構。2. The first plate member and the second plate member are connected to the input side plate member and the output side plate member, respectively, such that they cannot rotate relative to each other and are movable in the axial direction. Friction generation mechanism.
ート部材に軸方向に移動可能にかつ所定角度間で相対回
転可能に連結されている、請求項１に記載の摩擦発生機
構。3. The friction generating mechanism according to claim 1, wherein the first plate member is connected to the input side plate member so as to be movable in the axial direction and relatively rotatable at a predetermined angle.
能にかつ前記出力側プレート部材に所定角度間で相対回
転可能に連結されている、請求項１または３に記載の摩
擦発生機構。4. The friction generating mechanism according to claim 1, wherein the second plate member is coupled to the output side plate member so as to be movable in the axial direction and relatively rotatable at a predetermined angle.
と、前記第１環状部から軸方向に延び前記入力側プレー
ト部材に連結される複数の第１連結部とを有し、 前記第２プレート部材は、前記第２環状部と、前記第２
環状部から軸方向に延び前記出力側プレート部材に連結
される複数の第２連結部とを有している、請求項１〜４
のいずれかに記載の摩擦発生機構。5. The first plate member includes the first annular portion, and a plurality of first connecting portions extending axially from the first annular portion and connected to the input side plate member, The second plate member includes the second annular portion and the second annular portion.
5. A plurality of second connecting portions extending in the axial direction from the annular portion and connected to the output side plate member are included.
The friction generating mechanism according to any one of 1.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15624695A JP3434389B2 (en) | 1995-06-22 | 1995-06-22 | Friction generating mechanism |
| DE19624684A DE19624684A1 (en) | 1995-06-22 | 1996-06-20 | Torsion damper in vehicle clutch |
| KR1019960022842A KR970002021A (en) | 1995-06-22 | 1996-06-21 | Friction generator |
| FR9607764A FR2735826A1 (en) | 1995-06-22 | 1996-06-21 | FRICTION GENERATOR MECHANISM, ESPECIALLY FOR A DAMPER DISC ASSEMBLY |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15624695A JP3434389B2 (en) | 1995-06-22 | 1995-06-22 | Friction generating mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH094680A true JPH094680A (en) | 1997-01-07 |
| JP3434389B2 JP3434389B2 (en) | 2003-08-04 |
Family
ID=15623582
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15624695A Expired - Fee Related JP3434389B2 (en) | 1995-06-22 | 1995-06-22 | Friction generating mechanism |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP3434389B2 (en) |
| KR (1) | KR970002021A (en) |
| DE (1) | DE19624684A1 (en) |
| FR (1) | FR2735826A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002181131A (en) * | 2000-12-12 | 2002-06-26 | Valeo Unisia Transmission Kk | Torque transmission |
| JP2004092820A (en) * | 2002-09-02 | 2004-03-25 | Exedy Corp | Frictional resistance generating mechanism |
| US7195111B2 (en) | 2002-09-02 | 2007-03-27 | Exedy Corporation | Clutch device having a clutch damper and dual-mass flywheel assembly |
| US7800674B2 (en) | 2003-04-02 | 2010-09-21 | Olympus Corporation | Solid-state image sensing apparatus and method of reading image signal using a plurality of output channels |
| WO2018037827A1 (en) * | 2016-08-24 | 2018-03-01 | 株式会社エクセディ | Vibration reduction device |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR3073587B1 (en) * | 2017-11-10 | 2021-04-23 | Valeo Embrayages | CLUTCH FRICTION DEVICE |
| KR102281574B1 (en) * | 2019-07-17 | 2021-07-26 | 아주산업 주식회사 | the improved production system for PHC pile |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2370902A1 (en) * | 1976-11-15 | 1978-06-09 | Ferodo Sa | TORSION DAMPER DEVICE, ESPECIALLY FOR MOTOR VEHICLE CLUTCHES, AND UNIT SUBASSEMBLY SPECIFIC TO CONSTITUTING SUCH A DEVICE |
| DE3502229A1 (en) * | 1985-01-24 | 1986-07-24 | Fichtel & Sachs Ag, 8720 Schweinfurt | INDIRECT STORAGE FOR A SHARED FLYWHEEL |
| DE8509108U1 (en) * | 1985-03-27 | 1992-12-10 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Device for compensating torsional shocks |
| JPH076545B2 (en) * | 1986-09-30 | 1995-01-30 | アイシン精機株式会社 | Torque fluctuation absorber |
| FR2609132B1 (en) * | 1986-12-24 | 1991-03-08 | Valeo | SHOCK ABSORBER FOR TRANSMISSION, ESPECIALLY FOR MOTOR VEHICLES |
| JPH0792114B2 (en) * | 1987-04-15 | 1995-10-09 | 株式会社大金製作所 | Flywheel assembly |
-
1995
- 1995-06-22 JP JP15624695A patent/JP3434389B2/en not_active Expired - Fee Related
-
1996
- 1996-06-20 DE DE19624684A patent/DE19624684A1/en not_active Withdrawn
- 1996-06-21 KR KR1019960022842A patent/KR970002021A/en not_active Application Discontinuation
- 1996-06-21 FR FR9607764A patent/FR2735826A1/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002181131A (en) * | 2000-12-12 | 2002-06-26 | Valeo Unisia Transmission Kk | Torque transmission |
| JP2004092820A (en) * | 2002-09-02 | 2004-03-25 | Exedy Corp | Frictional resistance generating mechanism |
| US7195111B2 (en) | 2002-09-02 | 2007-03-27 | Exedy Corporation | Clutch device having a clutch damper and dual-mass flywheel assembly |
| US7800674B2 (en) | 2003-04-02 | 2010-09-21 | Olympus Corporation | Solid-state image sensing apparatus and method of reading image signal using a plurality of output channels |
| WO2018037827A1 (en) * | 2016-08-24 | 2018-03-01 | 株式会社エクセディ | Vibration reduction device |
| JP2018031426A (en) * | 2016-08-24 | 2018-03-01 | 株式会社エクセディ | Vibration reduction device |
Also Published As
| Publication number | Publication date |
|---|---|
| KR970002021A (en) | 1997-01-24 |
| DE19624684A1 (en) | 1997-01-02 |
| JP3434389B2 (en) | 2003-08-04 |
| FR2735826A1 (en) | 1996-12-27 |
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| LAPS | Cancellation because of no payment of annual fees |