JPS61252959A - Directly-coupled clutch for hydraulic transmission - Google Patents

Directly-coupled clutch for hydraulic transmission

Info

Publication number
JPS61252959A
JPS61252959A JP9345485A JP9345485A JPS61252959A JP S61252959 A JPS61252959 A JP S61252959A JP 9345485 A JP9345485 A JP 9345485A JP 9345485 A JP9345485 A JP 9345485A JP S61252959 A JPS61252959 A JP S61252959A
Authority
JP
Japan
Prior art keywords
buffer member
plate
plates
buffer
pair
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.)
Pending
Application number
JP9345485A
Other languages
Japanese (ja)
Inventor
Kazumasa Tsukamoto
一雅 塚本
Masahiro Hayabuchi
正宏 早渕
Koji Maeda
浩司 前田
Kazuaki Watanabe
和昭 渡辺
Yutaka Taga
豊 多賀
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin AW Co Ltd
Toyota Motor Corp
Original Assignee
Aisin AW Co Ltd
Toyota Motor Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Aisin AW Co Ltd, Toyota Motor Corp filed Critical Aisin AW Co Ltd
Priority to JP9345485A priority Critical patent/JPS61252959A/en
Priority to US06/856,815 priority patent/US4716998A/en
Publication of JPS61252959A publication Critical patent/JPS61252959A/en
Pending legal-status Critical Current

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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

PURPOSE:To reduce fluctuation of spring constant by forming a driven plate with a pair of plates containing a buffer member while holding the drive plate between a pair of plates and providing an energizing projection on said plate. CONSTITUTION:Driven plate 27 is formed with first guide plate 25 having outer and inner circumference buffer member holding frames 25A, 26A, 25B, 26B and second guide plate 26 while the drive plate 28 is held slidably between the first and second guide plates 25, 26 and innercircumference buffer member energizing projection 283 is provided on the drive plate 28. Since the sliding section of the drive plate 28 and the driven plate 27 can be limited only on the circumference of one buffer member in two group buffer members, the sliding resistance can be reduced resulting in reduction of fluctuation of spring constant.

Description

【発明の詳細な説明】 ［産業上の利用分野］ 本発明は、流体伝動装置の直結クラッチに関する。[Detailed description of the invention] [Industrial application field] The present invention relates to a direct coupling clutch for a fluid transmission device.

［従来の技術］ 車両に搭載されたエンジンの出力を入力とする入力部材
と変速機構に出力する出力部材との間に流体を介して連
結する流体伝動装置の入力部材と着脱自在に係合するピ
ストンと、該ピストンと連結するドライブプレート、該
ドライブプレートと緩衝部材を介して連結された流体伝
動装置の出力部材と連結するドリブンプレートからなる
ダンパ機構とからなる流体伝動装置の直結クラッチは、
ドリブンプレートの外周側の同一円周上に２種のスプリ
ングを配設して設けていた。しかるに近年のエンジンの
高出力化によりダンパ機構の径を大きくすることなく、
吸収できるトルク変動の範囲を大きくすることが要求さ
れているが、従来のダンパ機構は同一円周上に２種類の
緩衝部材を配設するため、捩り角が小さく、トルクを吸
収できる範囲が狭い範囲に限定されていたため、巾広い
トルク変動に対応すべく、捩り角の範囲を大きく取れる
よう、２種の緩衝部材を流体伝動装置の外周側とその内
周に設けたダンパ機構が提案されている（　ＵＳＰ４．
３１８．００３、ＵＳＰ４．３４７．７１７、特開昭５
７−１９５９５７）。この流体伝動装置の外周側の！！
衝郡部材両側より包み込んで保持する一対のプレートお
よび内周側の緩衝部材を両側より包み込んで保持する一
対のプレートは、それぞれ一対のプレートの間にドライ
ブプレートあるいはドリブンプレートを保持し、外周お
よび内周の緩衝部材を介して連結されていた。[Prior Art] An input member that receives the output of an engine mounted on a vehicle and is removably engaged with an input member of a fluid transmission device that is connected via fluid between an input member that inputs the output of an engine mounted on a vehicle and an output member that outputs output to a transmission mechanism. A direct coupling clutch for a fluid transmission device includes a piston, a drive plate connected to the piston, and a damper mechanism including a driven plate connected to an output member of the fluid transmission device connected to the drive plate via a buffer member.
Two types of springs were arranged on the same circumference on the outer peripheral side of the driven plate. However, due to the increase in the output of engines in recent years, it is not necessary to increase the diameter of the damper mechanism.
There is a need to widen the range of torque fluctuations that can be absorbed, but because conventional damper mechanisms have two types of buffer members arranged on the same circumference, the torsion angle is small and the range in which torque can be absorbed is narrow. Therefore, in order to accommodate wide torque fluctuations, a damper mechanism was proposed in which two types of buffer members were installed on the outer circumference of the fluid transmission device and on the inner circumference of the fluid transmission device in order to accommodate a wide range of torsional angles. (USP4.
318.003, USP4.347.717, JP-A-5
7-195957). The outer circumferential side of this fluid transmission device! !
A pair of plates that wrap and hold the buffer member on both sides, and a pair of plates that wrap and hold the buffer member on the inner circumference from both sides, each hold a drive plate or driven plate between the pair of plates. They were connected via a surrounding buffer member.

［発明が解決しようとする問題点］ 上記に示す従来の技術では、外周緩衝部材の保持部およ
び内周緩衝部材の保持部のそれぞれの周上でドライブプ
レートとドリブンプレートとが摺動されるため、摺動抵
抗が大きくされ、外周緩衝部材および内周緩衝部材の動
バネ常数が大きくされ、外周および内周緩衝部材のバネ
常数が摺動抵抗により大きく変化する問題点を有してい
た。[Problems to be Solved by the Invention] In the conventional technology described above, the drive plate and the driven plate slide on the respective peripheries of the holding portion of the outer circumferential buffer member and the holding portion of the inner circumferential buffer member. , the sliding resistance was increased and the dynamic spring constants of the outer and inner cushioning members were increased, and the spring constants of the outer and inner cushioning members changed greatly due to the sliding resistance.

本発明の目的は、捩り角の範囲が大きくとれ、且つコン
パクトで緩衝部材の振動レベルの低いダンパ機構を有す
る流体伝動装置の直結クラッチの提供にある。SUMMARY OF THE INVENTION An object of the present invention is to provide a direct coupling clutch for a fluid transmission device that has a large torsion angle range, is compact, and has a damper mechanism with a low vibration level of a buffer member.

［問題点を解決するための手段］ 上記問題点を解決すべく、本発明の流体伝動装置の直結
クラッチは、流体伝動装置の入力部材と着脱自在に係合
するピストンと、外周と内周とに同心的に配設される２
群の緩衝部材、該２群の緩衝部材を両側から包み込む一
対のプレート、該一対のプレートを連結する連結手段、
前記２群の緩衝部材のうち、一方の緩衝部材が配設され
る周上で前記一対のプレート間に保持され、他方の緩衝
部材が配設される周上に突出して前記他方の緩衝部材を
付勢する付勢突起を有し、前記２群の緩衝部材を介して
前記一対のプレートと連結されるプレートからなり、前
記一対のプレートおよびプレートのうち一方のプレート
が前記ピストンと連結し、他方のプレートが出力部材と
連結するダンパ機構とから構成される。[Means for Solving the Problems] In order to solve the above problems, the direct coupling clutch of the fluid transmission device of the present invention includes a piston that removably engages with an input member of the fluid transmission device, an outer periphery and an inner periphery. 2 arranged concentrically in
a group of buffer members, a pair of plates that wrap around the two groups of buffer members from both sides, and a connecting means that connects the pair of plates;
Among the two groups of buffer members, one of the buffer members is held between the pair of plates on the circumference where the other buffer member is disposed, and protrudes onto the circumference where the other buffer member is disposed to protect the other buffer member. a plate having a biasing protrusion for biasing and connected to the pair of plates via the two groups of buffer members, one plate of the pair of plates and the plate being connected to the piston, and the other plate being connected to the piston; The plate is composed of a damper mechanism connected to an output member.

［作用および発明の効果］ 上記構成よりなる本発明の流体伝動装置の直結クラッチ
は、外周と内周に緩衝部材が配設されるため、吸収でき
るトルク容量を大きくすることができる。従来と同様な
トルク吸収容量とする場合は、ダンパ機構の径を小さく
することができると共に、２群の緩衝部材のうち一方の
緩衝部材を付勢突起で付勢するよう設けることにより、
直結クラッチを軽量およびコンパクト化することができ
る。また、ドライブプレートあるいはドリブンプレート
のうちいずれか一方のプレートを、外周および内周緩衝
部材を内包する一対のプレートで形成し、他方のプレー
トを外周あるいは内周緩衝部材のいずれか一方の緩衝部
材の周上で前記一方のプレート間に保持され、他方の緩
衝部材を付勢する付勢突起を設けることにより、２群の
緩衝部材を有するダンパ機構のドライブプレートとドリ
ブンプレートの摺動部を、２群の緩衝部材のうち、一方
の緩衝部材の周上のみとすることができ、従来の２群の
緩衝部材を備えたダンパ機構に比べ、摺動抵抗を小さく
することができるため、２群の緩衝部材の動バネ常数を
小さくし、バネ常数の変動を小さくすることができる。[Operations and Effects of the Invention] Since the direct coupling clutch of the fluid transmission device of the present invention having the above-mentioned configuration has buffer members disposed on the outer circumference and the inner circumference, it is possible to increase the torque capacity that can be absorbed. In order to maintain the same torque absorption capacity as the conventional one, the diameter of the damper mechanism can be made smaller, and one of the two groups of buffer members is provided so as to be biased by a biasing protrusion.
A direct coupling clutch can be made lighter and more compact. In addition, either the drive plate or the driven plate is formed of a pair of plates containing the outer and inner buffer members, and the other plate is used as the outer or inner buffer member. By providing a biasing protrusion that is held between the one plate on the circumference and biases the other buffer member, the sliding portion of the drive plate and the driven plate of the damper mechanism having two groups of buffer members can be Among the buffer members in the group, only one of the buffer members can be placed on the circumference, and sliding resistance can be reduced compared to the conventional damper mechanism equipped with two groups of buffer members. The dynamic spring constant of the buffer member can be reduced, and fluctuations in the spring constant can be reduced.

［実施例］ つぎに本発明の流体伝動装置の直結クラッチを図に示す
一実施例に基づき説明する。[Embodiment] Next, a direct coupling clutch of a fluid transmission device of the present invention will be described based on an embodiment shown in the drawings.

第１図は本発明を適用した直結クラッチ付流体伝動装置
の断面図を示す。FIG. 1 shows a sectional view of a fluid transmission device with a direct coupling clutch to which the present invention is applied.

車両用自動変速機の動力伝達装置である直結クラッチ付
流体伝動装置は、トルクコンバータ１と直結クラッチ２
とからなり、トルクコンバータ１のケースである動力伝
達ケース１１と、該動力伝達ケース１１内で流体（作動
油）を介在させ、動力を伝達する流体伝動部１２とから
なり、直結クラッチ２は動力伝達ケース１１と流体伝動
部１２０間に配設され、直結クラッチ２は作動油供給手
段１３により駆動される。A fluid transmission device with a direct coupling clutch, which is a power transmission device for a vehicle automatic transmission, has a torque converter 1 and a direct coupling clutch 2.
It consists of a power transmission case 11 which is a case of the torque converter 1, and a fluid transmission part 12 that transmits power by interposing fluid (hydraulic oil) within the power transmission case 11. The direct coupling clutch 2 is disposed between the transmission case 11 and the fluid transmission section 120 and is driven by the hydraulic oil supply means 13 .

トルクコンバータ１は図示しないエンジンと図示しない
変速機構の間でトルクコンバータケース３１内に配設さ
れ、該トルクコンバータケース３１の後部（図示右側）
には変速機構を内設するトランスミッションケース３２
が締結され、トルクコンバータケース３１とトランスミ
ッションケース３２の間はオイルポンプハウジング３３
により隔壁されている。The torque converter 1 is disposed in a torque converter case 31 between an engine (not shown) and a transmission mechanism (not shown), and is located at the rear of the torque converter case 31 (on the right side in the figure).
A transmission case 32 in which a transmission mechanism is installed
are fastened, and an oil pump housing 33 is connected between the torque converter case 31 and the transmission case 32.
It is separated by walls.

動力伝達ケース１１は、エンジンのクランク軸４１とス
タータホイール４２を介して連結され、内部に直結クラ
ッチ２を内包するフロントカバー１１１と、該フロント
カバー１１１の内周に溶接された内部に流体伝動部１２
を内包する円環板状のりャカバー１１２と、該リアカバ
ー１１２の内周壁面の内壁に周設されたポンプ駆動スリ
ーブ１１３とから構成され、ポンプ駆動スリーブ１１３
の後端は、トルクコンバータケース３１とトランスミッ
ションケース３２の間に締結されたオイルポンプカバー
３３１の前方に突設して形成された筒状部３３１Ａ内と
メタルベアリング１３０Ａおよびオイルシール１３０Ｂ
を介して回転自在に内設され、オイルポンプカバー３３
１とリヤカバー３３２からなるオイルポンプハウジング
３３内に配設された外歯歯車５１と内歯歯車５２を備え
た内接歯車オイルポンプ５の外歯歯車５１を駆動すべく
、外歯歯車５１の内周とスプライン連結されている。The power transmission case 11 is connected to the crankshaft 41 of the engine via the starter wheel 42, and includes a front cover 111 that includes the direct coupling clutch 2 therein, and a fluid transmission section welded to the inner periphery of the front cover 111. 12
The pump drive sleeve 113 is composed of an annular plate-shaped rear cover 112 containing the rear cover 112 and a pump drive sleeve 113 provided around the inner wall of the rear cover 112.
The rear end is connected to the inside of a cylindrical portion 331A protruding from the front of an oil pump cover 331 fastened between the torque converter case 31 and the transmission case 32, a metal bearing 130A, and an oil seal 130B.
The oil pump cover 33 is rotatably installed inside the oil pump cover 33.
In order to drive the external gear 51 of the internal gear oil pump 5, which is provided with an external gear 51 and an internal gear 52, which are disposed in the oil pump housing 33 consisting of a rear cover 332 and a rear cover 332, It is connected to the circumference by a spline.

流体伝動部１２は、リヤカバー１１２の内部に一体に形
成され、リヤカバー１１２の回転により作動油を遠心力
で内周側から外周側に流動させるポンプ、羽根車１２１
と、該ポンプ羽根車１２１に対応して設けられ、ポンプ
羽根車１２１が外周側に流動させた作動油を受け、再び
内周側に流動させることによリボンブ羽根車１２１の回
転が伝達されるタービン羽根車１２２と、ポンプ羽根車
１２１とタービン羽根車１２２の内周側の間で作動油の
流動方向を変更し、トルクを増大させるステータ１２３
とから構成される。ステータ１２３の内周には一方向の
み回転可能な一方向りラッヂ１２４のアウターレース１
２４＾と連結し、一方向クラッチ１２４のインナーレー
ス１２４Ｂは、トランスミッションケース３２と締結さ
れたオイルポンプハウジング３３のリヤカバー３３２と
連結された固定スリーブ１２５の前端外周とスプライン
嵌合され、ステータ１２３を通過する作動油の流れの向
きにより一方向にのみ回転するように設けられている。The fluid transmission unit 12 is integrally formed inside the rear cover 112, and includes a pump and an impeller 121 that causes hydraulic oil to flow from the inner circumferential side to the outer circumferential side by centrifugal force as the rear cover 112 rotates.
The rotation of the ribbon impeller 121 is transmitted by receiving the hydraulic oil that the pump impeller 121 has caused to flow toward the outer circumference and causing it to flow toward the inner circumference again. A stator 123 that changes the flow direction of hydraulic oil between the turbine impeller 122 and the inner peripheral sides of the pump impeller 121 and the turbine impeller 122 to increase torque.
It consists of On the inner periphery of the stator 123 is an outer race 1 of a one-way latch 124 that can rotate in only one direction.
24^, the inner race 124B of the one-way clutch 124 is spline-fitted with the front end outer periphery of the fixed sleeve 125 connected to the rear cover 332 of the oil pump housing 33 which is connected to the transmission case 32, and passes through the stator 123. It is provided so that it can rotate only in one direction depending on the direction of the flow of hydraulic oil.

またタービン羽根車１２２を支持するタービンフランジ
１２２Ａは、固定スリーブ１２５の内周の前端と後端で
メタルベアリング１３０Ｃ，１３００を介して配設され
たトルクコンバータ１の出力部材である出力軸１２６と
中心側がスプライン連結される出力軸連結ハブ１２７の
外周フランジ１２７Ａと下達する直結クラッチの第２ガ
イドプレート２６の内周部と共にリベット１２８で固定
連結されている。Further, the turbine flange 122A supporting the turbine impeller 122 is centered with the output shaft 126, which is the output member of the torque converter 1, which is disposed via metal bearings 130C, 1300 at the front and rear ends of the inner circumference of the fixed sleeve 125. The outer periphery flange 127A of the output shaft connection hub 127, whose sides are spline-connected, is fixedly connected with the inner periphery of the second guide plate 26 of the direct-coupled clutch by a rivet 128.

直結クラッチ２は、第２図および第３図にも示す如く、
動力伝達ケース１１のフロントカバー１１１と流体伝動
部１２のタービン羽根車１２２の間に配設され、内周側
筒状部２１１、外周側筒状部２１２、円環状板部２１３
からなり、トルクコンバータ１の入力部材である動力伝
達ケース１１のフロントカバー１１１と着脱自在に係合
される円板状のピストン２１と、第４図および第５図に
示すロックアツプ係合時の衝撃を吸収するダンパ機構２
２とからなる。ピストン２１は内周側筒状部２１１が出
力軸連結ハブ１２７の環状凹部１２７Ｂにシールリング
１２７Ｃを介して軸方向に摺動自在に外嵌されている。The direct coupling clutch 2, as shown in FIGS. 2 and 3,
Arranged between the front cover 111 of the power transmission case 11 and the turbine impeller 122 of the fluid transmission section 12, the inner circumferential side cylindrical part 211, the outer circumferential side cylindrical part 212, and the annular plate part 213
A disk-shaped piston 21 is removably engaged with the front cover 111 of the power transmission case 11, which is an input member of the torque converter 1, and an impact during lock-up engagement shown in FIGS. 4 and 5. Damper mechanism 2 that absorbs
It consists of 2. The inner cylindrical portion 211 of the piston 21 is externally fitted into the annular recess 127B of the output shaft connection hub 127 via a seal ring 127C so as to be slidable in the axial direction.

円環状板部２１３は外周側がフロントカバー１１１の内
部に設けられたロックアツプ係合時に摩擦力を増大さぜ
る摩擦Ｕ２１Ａに対応した平面リング状のロックアツプ
係合面２１３Ａとして形成され、外周側筒状部２１２は
後方に開口する複数の切欠きを有するスプライン２１２
Ａが形成されている。The annular plate portion 213 has a flat ring-shaped lock-up engagement surface 213A provided inside the front cover 111 that increases the frictional force at the time of lock-up engagement, and a cylindrical surface on the outer circumference. The portion 212 is a spline 212 having a plurality of notches opening rearward.
A is formed.

ダンパ機構２２は、外周側にばね定数が小さく、ストロ
ーク長の大きい圧縮コイルスプリングよりなる一部の外
周緩衝部材２３、該外周緩衝部材２３の内周にばね定数
が大きく、ストローク長の小さい圧縮コイルスプリング
よりなる一部の内周緩衝部材２４を内包して周方向に摺
動自在に保持する外周スプリングハウス２３Ａ１内周ス
プリングハウス２４Ａを形成する第６図から第９図にも
示す第１外周緩衝部材保持枠２５Ａおよび第１内周緩衝
部材保持枠２５Ｂを備えた第１ガイドプレート２５、第
２外周緩衝部材保持枠２６Ａおよび第２内周緩衝部材保
持枠２６Ｂを備えた第２ガイドプレート２６よりなるド
リブンプレート２７と、第１０図および第１１図にも示
す如く、外周が前記外周筒状部２１２のスプライン２１
２Ａとスプライン嵌合されるスプライン２８１を有し、
外周スプリングハウス２３Ａ部の第１ガイドプレート２
５と第２ガイドプレート２６の間で周方向に摺動自在に
保持され、内部に外周緩衝部材２３を配設すると共に外
周！１Ｗｉ１部材２３をドリブンプレート２７の摺動に
より付勢する外周緩衝部材付勢窓２８２を有し、内周に
内周緩衝部材２４を付勢する内周緩衝部材付勢突起２８
３を有するドライブプレート２８とからなり、内周スプ
リングハウス２４Ａを形成する第１ガイドプレート２５
の第１内周緩衝部材保持枠２５Ｂは図示右回転方向が開
口して設けられ、内周緩衝部材２４が内周緩衝部材付勢
突起２８３方向に一部突設して設けられ、ドリブンプレ
ート２７とドライブプレート２８の周方向の摺動範囲（
捩り角）が−βとγの間とされており、捩り角δとγと
の間にて内周緩衝部材付勢突起２８３が内周スプリング
ハウス２４Ａより突出した内周緩衝部材２４を押圧する
よう設けられ、第１ガイドプレート２５と第２ガイドプ
レート２６は外周緩衝部材２３と内周緩衝部材２４の中
間部とされる周方向で、外周緩衝部材２３のほぼ中央部
位でリベット２９で固着され、ダンパ機構２２が形成さ
れている。前記ドライブプレート２８の外周に形成され
るスプライン２８１は外周緩衝部材２３のほぼ中央部位
とされ、ピストン２１の外周側筒状部２１２のスプライ
ン２１２＾は、ドライブプレート２８のスプライン２８
１に対応して形成されている。またドリブンプレート２
７の第２ガイドプレート２６は、上述の如く内周が出力
軸連結ハブ１２７に連結されている。The damper mechanism 22 includes a part of an outer periphery buffer member 23 made of a compression coil spring with a small spring constant and a large stroke length on the outer periphery side, and a compression coil with a large spring constant and a small stroke length on the inner periphery of the outer periphery buffer member 23. A first outer circumferential shock absorber also shown in FIGS. 6 to 9 forming an outer circumferential spring house 23A1 and an inner circumferential spring house 24A that encloses a part of the inner circumferential shock absorbing member 24 made of a spring and holds it slidably in the circumferential direction. From the first guide plate 25 including the member holding frame 25A and the first inner buffer member holding frame 25B, and the second guide plate 26 including the second outer buffer member holding frame 26A and the second inner buffer member holding frame 26B. As shown in FIG. 10 and FIG.
It has a spline 281 that is spline-fitted with 2A,
First guide plate 2 of outer spring house 23A section
5 and the second guide plate 26 in a slidable manner in the circumferential direction, and an outer periphery buffer member 23 is disposed inside and the outer periphery! An inner buffer member biasing protrusion 28 has an outer buffer member biasing window 282 that biases the 1Wi1 member 23 by sliding of the driven plate 27 and urges the inner buffer member 24 on the inner periphery.
3 and a first guide plate 25 forming an inner spring house 24A.
The first inner buffer member holding frame 25B is provided with an opening in the clockwise rotation direction in the figure, and the inner buffer member 24 is provided so as to partially protrude in the direction of the inner buffer member biasing protrusion 283, and the driven plate 27 and the circumferential sliding range of the drive plate 28 (
The torsion angle) is between -β and γ, and between the torsion angles δ and γ, the inner buffer member biasing protrusion 283 presses the inner buffer member 24 protruding from the inner spring house 24A. The first guide plate 25 and the second guide plate 26 are fixed with a rivet 29 at a substantially central portion of the outer buffer member 23 in the circumferential direction, which is an intermediate portion between the outer buffer member 23 and the inner buffer member 24. , a damper mechanism 22 is formed. The spline 281 formed on the outer periphery of the drive plate 28 is located approximately at the center of the outer periphery buffer member 23, and the spline 212^ of the outer cylindrical portion 212 of the piston 21 is formed on the spline 28 of the drive plate 28.
1. Also driven plate 2
As described above, the inner circumference of the second guide plate 26 of No. 7 is connected to the output shaft connection hub 127.

作動油供給手段１３は、オイルポンプハウジング３３の
リヤカバー３３２内に形成された油路１３１、該油路１
３１に対応して固定スリーブ１２５に形成された油路１
３２、出力軸１２６と固定スリーブ１２５の間でメタル
ベアリング１３０Ｃ，１３００の間に形成された油路１
３３、該油路１３３と油路１３４を介して連通し、　　
　　′出力軸１２６の軸心に形成された油路１３５、該
油路１３５と連通し、フロントカバー１１１とピストン
２１の間にて形成される油路１３６からなる第１油路１
３Ａと、ポンプ駆動スリーブ１１３と固定スリーブ１２
５の間に連通するオイルポンプハウジング３３のオイル
ポンプカバー３３１に形成された図示しない油路、ポン
プ駆動スリーブ１１３と固定スリーブ１２５の間に形成
された油路１３７、該油路１３７に連通し、ポンプ駆動
スリーブ１１３と一方向クラッチの１２４の間を通り、
ステータ１２３とポンプ羽根車１２１の間に連通する油
路１３８からなる第２油路１３Ｂとが形成されており、
第１油路１３Ａと第２油路１３Ｂの作動油の供給方向の
切換は図示しない油圧制御装置により行われ、その−六
個が選択されて油圧源と連結されるとその他方側から作
動油が排出される。The hydraulic oil supply means 13 includes an oil passage 131 formed in the rear cover 332 of the oil pump housing 33;
Oil passage 1 formed in fixed sleeve 125 corresponding to 31
32. Oil passage 1 formed between metal bearings 130C and 1300 between output shaft 126 and fixed sleeve 125
33, communicating via the oil passage 133 and oil passage 134;
'A first oil passage 1 consisting of an oil passage 135 formed at the axis of the output shaft 126, and an oil passage 136 communicating with the oil passage 135 and formed between the front cover 111 and the piston 21.
3A, pump drive sleeve 113 and fixed sleeve 12
5, an oil passage (not shown) formed in the oil pump cover 331 of the oil pump housing 33, an oil passage 137 formed between the pump drive sleeve 113 and the fixed sleeve 125, communicating with the oil passage 137, Passing between the pump drive sleeve 113 and the one-way clutch 124,
A second oil passage 13B consisting of an oil passage 138 communicating with the stator 123 and the pump impeller 121 is formed,
Switching of the supply direction of hydraulic oil to the first oil passage 13A and the second oil passage 13B is performed by a hydraulic control device (not shown), and when one of the six is selected and connected to a hydraulic source, hydraulic oil is supplied from the other side. is discharged.

つぎに上記構成よりなる流体伝動装置の作動を説明する
。Next, the operation of the fluid transmission device having the above configuration will be explained.

前記油圧制御装置がロックアツプ状態に設定されていな
いとき。When the hydraulic control device is not set to a lock-up state.

作油供給手段１３は、油圧源より作動油を第１油路１３
Ａを介して動力伝達ケース１１内を充填し、第２油路１
３Ｂより作動油を排出せしめる循環通路を形成するよう
に設定される。The oil supply means 13 supplies hydraulic oil from the hydraulic source to the first oil path 13.
The inside of the power transmission case 11 is filled through A, and the second oil passage 1 is filled.
It is set so as to form a circulation passage for discharging hydraulic oil from 3B.

動力伝達ケース１１内への作動油の供給がフロントカバ
ー１１１とピストン２１の間を介して行われるため、フ
ロントカバー１１１に固着された摩擦材２１Ａとピスト
ン２１のロックアツプ係合面２１３Ａとは油圧差によっ
て引き離されて両者間の摩擦係合面は解放され、作動油
は摩擦材２１Ａとロックアツプ係合面２１３Ａの間を流
れて動力伝達ケース１１内を充填し、流体伝動部１２を
循環し、第２油路１３Ｂを通って排出される。このとき
クランク軸４１からスターターホイール４２、動力伝達
ケース１１を介してポンプ羽根車１２１に入力された出
力は流体伝動部１２内を循環する作動油の流体伝動によ
ってタービン羽根車１２２に伝達される。従って出力軸
１２６には流体伝動部１２のトルクコンバータの作用の
みに基づく回転トルクが出力され、直結クラッチ２はト
ルク伝達を行わない。Since hydraulic oil is supplied into the power transmission case 11 through the space between the front cover 111 and the piston 21, there is a hydraulic pressure difference between the friction material 21A fixed to the front cover 111 and the lock-up engagement surface 213A of the piston 21. The frictional engagement surface between the two is released, and the hydraulic fluid flows between the friction material 21A and the lockup engagement surface 213A, filling the power transmission case 11, circulating through the fluid transmission part 12, and releasing the frictional engagement surface between the two. 2 oil passage 13B. At this time, the output input from the crankshaft 41 to the pump impeller 121 via the starter wheel 42 and the power transmission case 11 is transmitted to the turbine impeller 122 by fluid transmission of the hydraulic oil circulating within the fluid transmission section 12. Therefore, rotational torque based only on the action of the torque converter of the fluid transmission section 12 is output to the output shaft 126, and the direct coupling clutch 2 does not transmit torque.

前記油圧制御装置がロックアツプ状態に設定されている
とき。When the hydraulic control device is set to a lock-up state.

作動油供給手段１３は、油圧源より作動油を第２油路１
３Ｂを介して動力伝達ケース１１内を充填し、第１油路
１３Ａより作動油を排出せしめる循環通路を形成するよ
う設定される。The hydraulic oil supply means 13 supplies hydraulic oil from a hydraulic source to the second oil path 1.
It is set to form a circulation passage that fills the inside of the power transmission case 11 via 3B and discharges hydraulic oil from the first oil passage 13A.

動力伝達ケース１１内への作動油の供給は流体伝動部１
２側より行われるため、動力伝達ケース１１内は作動油
の充填圧力より圧力が高まると共にフロントカバー１１
１とピストン２１の間の作動油が第１油路１３＾より排
出されるため、フロントカバー１１１に設けられた摩擦
材２１Ａとピストン２１のロックアツプ係合面２１３Ａ
が動力伝達ケース１１内の作動油の充填圧力により圧迫
されて係合し、その結果、クランク軸４１からスタータ
ーホイール４２を介して動力伝達ケース１１に伝達され
た出力は、摩擦材２１Ａ１ピストン２１、ダンパ機構２
２および出力軸連結ハブ１２１を介して出力軸１２６に
伝達され、これによりエンジンの回転出力が出力軸１２
６に直結的に伝達される。Hydraulic oil is supplied into the power transmission case 11 through the fluid transmission unit 1.
Since this is carried out from the 2nd side, the pressure inside the power transmission case 11 becomes higher than the filling pressure of the hydraulic oil, and the front cover 11
1 and the piston 21 is discharged from the first oil passage 13^, the friction material 21A provided on the front cover 111 and the lock-up engagement surface 213A of the piston 21
are compressed and engaged by the filling pressure of the hydraulic oil in the power transmission case 11, and as a result, the output transmitted from the crankshaft 41 to the power transmission case 11 via the starter wheel 42 is transmitted to the friction material 21A1 piston 21, Damper mechanism 2
2 and the output shaft connection hub 121 to the output shaft 126, whereby the rotational output of the engine is transmitted to the output shaft 126 through the output shaft connection hub 121.
6.

つぎにダンパ機構の特性を第４図および第１２図の実線
（α）を用いて説明する。Next, the characteristics of the damper mechanism will be explained using the solid line (α) in FIGS. 4 and 12.

エンジンは第４図中の矢印へ方向に回転駆動されるもの
である。ドライブプレート２８およびドリブンプレート
２７に応力が加わらないドライブプレート２８およびド
・ノブンプレート２７の位置（捩り角）をＯとする。こ
こで例えばロックアツプ保合時などドライブプレート２
８の回転トルクがドリブンプレート２７の回転トルクよ
り大きい場合、トルク差０からトルク差εの範囲では、
ばね定数の小さい外周緩衝部材２３の付勢力にて捩り角
０からδまでを対処し、トルク差εからトルク差εより
トルク差が大きいトルク差この範囲では、ばね定数の大
きい内周緩衝部材２４がドライブプレート２８の内周緩
衝部材付勢突起２８３に付勢されて外周緩衝部材２３と
内周緩衝部材２４が同時に作動されて捩り角δからγの
範囲内で対処する。また例えば車両走行中、ロックアツ
プ係合状態でエンジン回転が下がった場合など、ドリブ
ンプレート２７の回転トルクがドライブプレート２８の
回転トルクより大ぎい場合、トルク差０からトルク差η
の範囲を、ばね定数の小さい外周緩衝部材２３の付勢力
のみで捩り角０から−βまでを対処する。The engine is driven to rotate in the direction of the arrow in FIG. The position (torsion angle) of the drive plate 28 and the driven plate 27 where stress is not applied to the drive plate 28 and the driven plate 27 is O. Here, for example, when locking up, drive plate 2
When the rotational torque of 8 is larger than the rotational torque of the driven plate 27, in the range of torque difference 0 to torque difference ε,
The torsional angle from 0 to δ is handled by the biasing force of the outer peripheral buffer member 23 with a small spring constant, and the inner peripheral buffer member 24 with a large spring constant deals with the torque difference ε to a torque difference larger than the torque difference ε. is biased by the inner buffer member biasing protrusion 283 of the drive plate 28, and the outer buffer member 23 and inner buffer member 24 are actuated simultaneously to cope with the twist angle within the range of δ to γ. Further, when the rotational torque of the driven plate 27 is larger than the rotational torque of the drive plate 28, for example, when the engine speed decreases in the lock-up engagement state while the vehicle is running, the torque difference η changes from 0 to the torque difference η.
The range of torsion angles from 0 to -β can be handled only by the biasing force of the outer peripheral buffer member 23 having a small spring constant.

第１３図、第１４図および第１５図に本発明の他の実施
例を示す。Other embodiments of the present invention are shown in FIGS. 13, 14, and 15.

本実施例のダンパ機構２２８は、外周側にばね定数が小
さく、ストローク長の大きい圧縮コイルスプリングより
なる一部の外周緩衝部材２３ａをピストン２１の外周側
筒状部２１２の内周と共に保持する外周緩衝部材保持室
２３Ａａ、前記外周！ｆｉ！ｉ部材２３ａの内周にばね
定数が大きく、ストローク長の小さい圧縮コイルスプリ
ングよりなる一部の内周緩衝部材２４ａを保持する内周
緩衝部材保持室２４Ａａを形成する第１外周緩衝部材保
持枠２５Ａａおよび第１内周緩衝部材保持枠２５Ｂａを
備え、内周に前記出力軸連結ハブ１２７の外周に設けら
れたスプライン１２７０ａに対応したスプライン嵌合部
２５Ｃａが形成された第１ガイドプレート２５ａ１第２
外周緩衝部材保持枠２６Ａａおよび第２内周緩衝部材保
持枠２６Ｂａを備えた第２ガイドプレート２６ａよりな
り、第１ガイドプレート２５ａと第２ガイドプレート２
６ａは外周緩衝部材２３ａと内周緩衝部材２４ａの中間
部とされる周方向でリベット２９ａで固着され、第１ガ
イドプレート２５ａと第２ガイドプレート２６ａとが開
くのを防ぎ、外周緩衝部材２３ａおよび内周緩衝部材２
４ａが外周緩衝部材保持室２３Ａａおよび内周緩衝部材
保持室２４Ａａから飛び出すのを防ぐドリブンプレート
２７ａと、外周緩衝部材保持室２ａＡａ部の第１ガイド
プレート２５ａと第２ガイドプレート２６ａの間で周方
向に摺動自在に保持され、内部に外周ｗ１衝部材２３ａ
を配設すると共に外周緩衝部材２３ａをドリブンプレー
ト２７ａの摺動により付勢する外周緩衝部材付勢枠２８
２ａを有し、内周に内周緩衝部材２４ａを付勢する内周
緩衝部材付勢突起２８３ａを有するドライブプレート２
８ａとからなり、内周緩衝部材付勢突起２８３ａとピス
トン２１とがリベット３０ａにより固着され、ピストン
２１とドライブプレート２８ａとが連結されている。内
周緩衝部材保持室２４Ａａを形成する第１ガイドプレー
ト２５ａの第１内周緩衝部材保持枠２５Ｂａは図示左回
転方向が開口して内周緩衝部材２４ａが一部突設するよ
う設けられ、内周緩衝部材付勢突起２８３ａが内周緩衝
部材保持室２４Ａａより突出した内周緩衝部材２４ａを
押圧するよう設けられている。またドリブンプレート２
７ａの第１ガイドプレート２５ａの内周のスプライン嵌
合部２５Ｃａは、ダンパ機構２２ａが軸方向に摺動可能
とされるよう出力軸連結ハブ１２７のスプライン１２７
Ｄａとスプライン連結されている。The damper mechanism 228 of this embodiment has an outer periphery that holds a part of the outer periphery buffer member 23a made of a compression coil spring with a small spring constant and a large stroke length on the outer periphery side together with the inner periphery of the outer cylindrical part 212 of the piston 21. Buffer member holding chamber 23Aa, the outer periphery! Fi! A first outer buffer member holding frame 25Aa that forms an inner buffer member holding chamber 24Aa that holds a portion of the inner buffer member 24a made of a compression coil spring with a large spring constant and a small stroke length on the inner periphery of the i member 23a. and a first inner buffer member holding frame 25Ba, and a second guide plate 25a1 having a spline fitting portion 25Ca corresponding to the spline 1270a provided on the outer periphery of the output shaft connection hub 127 formed on the inner periphery.
Consisting of a second guide plate 26a including an outer buffer member holding frame 26Aa and a second inner buffer member holding frame 26Ba, the first guide plate 25a and the second guide plate 2
6a is fixed with a rivet 29a in the circumferential direction at an intermediate portion between the outer circumferential buffer member 23a and the inner circumferential buffer member 24a, and prevents the first guide plate 25a and the second guide plate 26a from opening. Inner peripheral buffer member 2
4a from the outer circumferential buffer member holding chamber 23Aa and the inner circumferential buffer member holding chamber 24Aa, and the first guide plate 25a and the second guide plate 26a of the outer circumferential buffer member holding chamber 2aAa section. The outer periphery w1 impact member 23a is held slidably inside the
an outer buffer member biasing frame 28 that urges the outer buffer member 23a by sliding of the driven plate 27a.
2a, and has an inner circumferential buffer member biasing protrusion 283a on the inner circumference that biases the inner circumferential buffer member 24a.
8a, the inner peripheral buffer member biasing protrusion 283a and the piston 21 are fixed by a rivet 30a, and the piston 21 and the drive plate 28a are connected. The first inner buffer member holding frame 25Ba of the first guide plate 25a forming the inner buffer member holding chamber 24Aa is opened in the left rotation direction in the drawing, and the inner buffer member 24a is partially protruded. The circumferential buffer member biasing protrusion 283a is provided to press the inner circumferential buffer member 24a protruding from the inner circumferential buffer member holding chamber 24Aa. Also driven plate 2
The spline fitting portion 25Ca on the inner circumference of the first guide plate 25a of 7a is connected to the spline 127 of the output shaft connection hub 127 so that the damper mechanism 22a can be slid in the axial direction.
It is spline connected to Da.

上記実施例では流体伝動装置にトルクコンバータを適用
した例を示したが、流体継手（フリユイドカップリング
）など他の流体伝動装置に適用しても良い。Although the above embodiment shows an example in which a torque converter is applied to a fluid transmission device, it may be applied to other fluid transmission devices such as a fluid coupling (fluid coupling).

上記実施例では外周緩衝部材および内周緩衝部材に圧縮
コイルスプリングを適用した例を示したが、他にリーフ
スプリング、テンションコイルスプリング、ゴム部材な
ど、他の緩衝部材を適用して用いても良い。また圧縮コ
イルスプリング内に圧縮コイルスプリングを配設したデ
ュアルコイルスプリング、圧縮コイルスプリングとゴム
部材とを組合せるなど、種々の緩衝部材を組合せて用い
ても良い。Although the above embodiment shows an example in which compression coil springs are applied to the outer and inner buffer members, other buffer members such as leaf springs, tension coil springs, rubber members, etc. may also be used. . Further, various shock absorbing members may be used in combination, such as a dual coil spring in which a compression coil spring is disposed within a compression coil spring, or a combination of a compression coil spring and a rubber member.

上記実施例では、外周および内周緩衝部材を両側から包
み込む一対のプレートにドリブンプレートを適用し、一
方の緩衝部材（上記実施例では内周緩衝部材）を付勢す
る付勢突起を有したプレートにドライブプレートを適用
した例を示したが、ドライブプレートに一対のプレート
を適用し、ドリブンプレートに付勢突起を有したプレー
トを適用して用いても良い。In the above embodiment, a driven plate is applied to a pair of plates that wrap around the outer and inner buffer members from both sides, and the plate has a biasing protrusion that biases one of the buffer members (the inner buffer member in the above embodiment). Although an example is shown in which a drive plate is used, a pair of plates may be used as the drive plate, and a plate having a biasing protrusion may be used as the driven plate.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明の流体伝動装置の直結クラッチを適用し
た第１実施例にかかる直結クラッチ付流体伝動装置の側
面断面図、第２図はピストンの正面図、−第３図はピス
トンの側面断面図、第４図はダンパ機構の正面図、第５
図は第４図に示すダンパ機構のＩ−■線に沿う断面図、
第６図は第１ガイドプレートの正面図、第７図は第６図
に示す第１ガイドプレートのＨ−Ｉ線に沿う断面図、第
８図は第２ガイドプレートの正面図、第９図は第８図に
示す第２ガイドプレートの■−■線に沿う断面図、第１
０図はドライブプレートの正面図、第１１図は第１０図
に示すドライブプレートのＩＶ−■線に沿う断面図、第
１２図は横軸にドライブプレートとドリブンプレートと
の捩り角、縦軸にトルクを示し、本発明の第１実施例に
がかるダンパ機構の特性を表すグラフ、第１３図は本発
明の第２実施例にかかる直結クラッチ付流体伝動装置の
側面断面図、第１４図は第１３図に示すダンパ機構の正
面図、第１５図は第１４図に示すダンパ機構のｖ−Ｖ線
に沿う断面図である。 図中　１・・・トルクコンバータ　２・・・直結クラッ
チ　１１・・・動力伝達ケース　２１・・・ピストン　
２２．２２ａ　−・・ダンパ゛機構　２３．２３ａ　・
・・外周１１！ｌ’ｊ部材　２４．２４ａ・・・内周緩
衝部材　２５．２５ａ・・・第１ガイドプレート　２６
．２６ａ・・・第２ガイドプレート　２γ、２７ａ・・
・ドリブンプレート　２８．２８ａ・・・ドライブプレ
ート　２９．２９ａ・・・リベット　１２６・・・出力
軸　１２７・・・出力軸連結ハブFig. 1 is a sectional side view of a fluid transmission device with a direct coupling clutch according to a first embodiment to which the direct coupling clutch of the fluid transmission device of the present invention is applied, Fig. 2 is a front view of the piston, and - Fig. 3 is a side view of the piston. A sectional view, Figure 4 is a front view of the damper mechanism, and Figure 5 is a front view of the damper mechanism.
The figure is a cross-sectional view of the damper mechanism shown in Figure 4, taken along line I-■.
FIG. 6 is a front view of the first guide plate, FIG. 7 is a sectional view of the first guide plate shown in FIG. 6 along line H-I, FIG. 8 is a front view of the second guide plate, and FIG. is a cross-sectional view of the second guide plate along the line ■-■ shown in FIG.
Figure 0 is a front view of the drive plate, Figure 11 is a cross-sectional view of the drive plate shown in Figure 10 along the line IV-■, and Figure 12 shows the torsion angle between the drive plate and the driven plate on the horizontal axis and the vertical axis. A graph showing the torque and representing the characteristics of the damper mechanism according to the first embodiment of the present invention, FIG. 13 is a side sectional view of the fluid transmission device with a direct coupling clutch according to the second embodiment of the present invention, and FIG. FIG. 13 is a front view of the damper mechanism shown in FIG. 13, and FIG. 15 is a cross-sectional view of the damper mechanism shown in FIG. 14 taken along line V-V. In the diagram 1... Torque converter 2... Direct clutch 11... Power transmission case 21... Piston
22.22a - Damper mechanism 23.23a ・
...Outer circumference 11! l'j member 24.24a... Inner peripheral buffer member 25.25a... First guide plate 26
．． 26a...Second guide plate 2γ, 27a...
・Driven plate 28.28a... Drive plate 29.29a... Rivet 126... Output shaft 127... Output shaft connection hub

Claims (1)

【特許請求の範囲】 １）流体伝動装置の入力部材と着脱自在に係合するピス
トンと、外周と内周とに同心的に配設される２群の緩衝
部材、該２群の緩衝部材を両側から包み込む一対のプレ
ート、該一対のプレートを連結する連結手段、前記２群
の緩衝部材のうち、一方の緩衝部材が配設される周上で
前記一対のプレート間に保持され、他方の緩衝部材が配
設される周上に突出して前記他方の緩衝部材を付勢する
付勢突起を有し、前記２群の緩衝部材を介して前記一対
のプレートと連結されるプレートからなり、前記一対の
プレートおよびプレートのうち一方のプレートが前記ピ
ストンと連結し、他方のプレートが出力部材と連結する
ダンパ機構とからなる流体伝動装置の直結クラツチ。 ２）前記一対のプレートは、前記流体伝動装置の出力部
材と連結するドリブンプレートであり、前記プレートは
、前記ピストンと連結するドライブプレートであること
を特徴とする特許請求の範囲第１項記載の流体伝動装置
の直結クラツチ。 ３）前記付勢突起は、前記２群の緩衝部材のうち、内周
の緩衝部材を付勢するよう設けられたことを特徴とする
特許請求の範囲第１項または第２項記載の流体伝動装置
の直結クラツチ。 ４）前記付勢突起の緩衝部材を付勢する押圧面は、前記
緩衝部材の当接面に対応した形状とされたことを特徴と
する特許請求の範囲第１項ないし第３項のいずれかに記
載の流体伝動装置の直結クラツチ。[Scope of Claims] 1) A piston that removably engages with an input member of a fluid transmission device, two groups of buffer members arranged concentrically on an outer periphery and an inner periphery, and the two groups of buffer members. A pair of plates that wrap around from both sides, a connecting means that connects the pair of plates, a connecting means that is held between the pair of plates on the circumference where one of the two groups of buffer members is disposed, and a connecting means that connects the pair of plates; The plate has a biasing protrusion that protrudes on the periphery where the member is disposed and biases the other buffer member, and is connected to the pair of plates via the two groups of buffer members, and a damper mechanism in which one of the plates is connected to the piston and the other plate is connected to the output member. 2) The pair of plates are driven plates connected to an output member of the fluid transmission device, and the plate is a drive plate connected to the piston. Direct coupling clutch for fluid transmission devices. 3) The fluid transmission according to claim 1 or 2, wherein the biasing protrusion is provided to bias an inner peripheral buffer member of the two groups of buffer members. Direct coupling clutch of the device. 4) Any one of claims 1 to 3, characterized in that the pressing surface of the biasing protrusion that biases the buffer member has a shape corresponding to the contact surface of the buffer member. A direct coupling clutch for a fluid transmission device as described in .
JP9345485A 1985-04-30 1985-04-30 Directly-coupled clutch for hydraulic transmission Pending JPS61252959A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP9345485A JPS61252959A (en) 1985-04-30 1985-04-30 Directly-coupled clutch for hydraulic transmission
US06/856,815 US4716998A (en) 1985-04-30 1986-04-28 Direct coupling clutch with a damper device for a fluid coupling

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP9345485A JPS61252959A (en) 1985-04-30 1985-04-30 Directly-coupled clutch for hydraulic transmission

Publications (1)

Publication Number Publication Date
JPS61252959A true JPS61252959A (en) 1986-11-10

Family

ID=14082769

Family Applications (1)

Application Number Title Priority Date Filing Date
JP9345485A Pending JPS61252959A (en) 1985-04-30 1985-04-30 Directly-coupled clutch for hydraulic transmission

Country Status (1)

Country Link
JP (1) JPS61252959A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02225860A (en) * 1989-12-27 1990-09-07 Aisin Aw Co Ltd Direct-coupled clutch for hydraulic power transmission
JPH02225861A (en) * 1989-12-27 1990-09-07 Aisin Aw Co Ltd Direct-coupled clutch for hydraulic power transmission
JPH02225859A (en) * 1989-12-27 1990-09-07 Aisin Aw Co Ltd Direct-coupled clutch for hydraulic power transmission

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02225860A (en) * 1989-12-27 1990-09-07 Aisin Aw Co Ltd Direct-coupled clutch for hydraulic power transmission
JPH02225861A (en) * 1989-12-27 1990-09-07 Aisin Aw Co Ltd Direct-coupled clutch for hydraulic power transmission
JPH02225859A (en) * 1989-12-27 1990-09-07 Aisin Aw Co Ltd Direct-coupled clutch for hydraulic power transmission

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