JPS5830531A - Friction clutch - Google Patents
Friction clutchInfo
- Publication number
- JPS5830531A JPS5830531A JP12833081A JP12833081A JPS5830531A JP S5830531 A JPS5830531 A JP S5830531A JP 12833081 A JP12833081 A JP 12833081A JP 12833081 A JP12833081 A JP 12833081A JP S5830531 A JPS5830531 A JP S5830531A
- Authority
- JP
- Japan
- Prior art keywords
- facing
- pushing
- clutch
- piston
- pressing member
- 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
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
- F16H2045/0273—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)
Abstract
Description
【発明の詳細な説明】
自動車用自動変速機に用いられるトルクコンバータのポ
ンプとタービンとの間に設けられて運転状態に応じてポ
ンプとタービンを直結する摩擦クラッチにおいて、従来
では、ピストンは環状体で構成され、その外周部におい
てクラッチフエーシングと係合するように゛なっている
ので、ピストンに加わる油圧の作用中心とクラッチの負
荷中心とがオフセットしており、その結果フエーシング
に対しピストンが内径側で片当りを起し、摩擦接触半径
の減少にＬるトルク容量の低下、クラッチの偏摩耗、フ
ェーシングの摩擦面での面圧の局部的増大による摩擦特
性の劣化、即ち静摩擦と動摩擦の差の増大に：るクラッ
チジャダ−の発生等の不具合が生じる。DETAILED DESCRIPTION OF THE INVENTION In a friction clutch that is provided between a pump and a turbine of a torque converter used in an automatic transmission for an automobile and directly connects the pump and turbine depending on the operating condition, conventionally, the piston is an annular body. The outer circumference of the piston engages with the clutch facing, so the center of action of the hydraulic pressure applied to the piston is offset from the load center of the clutch. This causes uneven contact on the side, decreases the frictional contact radius and decreases the torque capacity, uneven wear of the clutch, and deteriorates the friction characteristics due to a local increase in surface pressure on the friction surface of the facing, i.e., the difference between static friction and dynamic friction. Due to the increase in the number of clutches, problems such as clutch judder occur.
作動のピストンを有する摩擦クラッチ９において、上記
ピストンが上記クラッチフェーシングを押付ける７工ー
シング押付部材及び同押付部材と密封的に接触する油圧
骨は部材で構成され、上記油圧骨は部材に当接する上記
７工ーシング押付部材の押子部分と゛上記クラッチ７エ
ーシングの押圧中心とを一致させるようにしたことを特
徴とする摩擦クラッチを提案するものである。In a friction clutch 9 having an actuating piston, the piston presses the clutch facing, and a hydraulic bone in sealing contact with the pressing member and the pressing member is composed of a member, and the hydraulic bone abuts the member. The present invention proposes a friction clutch characterized in that the pusher portion of the seven pressing member and the pressing center of the clutch seven acing are made to coincide with each other.
上記構成により、フェーシング押付部材の押圧部分の中
心とクラッチ７エーシングの押土中心とが一致している
ので、フェーシングとフェーシング押付部材との均一な
摩擦接触が行われ、上記不具合を解消できる。With the above configuration, the center of the pressing portion of the facing pressing member and the center of the pressing part of the clutch 7 acing match, so that uniform frictional contact between the facing and the facing pressing member is achieved, and the above-mentioned problem can be solved.
以下１８本発明の実施例を添付図面を参照して詳細に説
明する。Hereinafter, eighteen embodiments of the present invention will be described in detail with reference to the accompanying drawings.
第７図において、自動車用自動変速機に用いられた摩擦
クラッチ２を備えたトルクコンバータｑが示されており
、こめ摩擦クラッチ２は常時スリップを生じながら動力
の伝達を行うスリップ式クラッチであって、クラッチの
保合時にはエンジンの多ランク軸６からの動力は主に同
クラッチを介して出力軸ｇに伝達され、一部の動力がト
ルクコンバータｌＩ’ｌ介して伝達され、従ってトルク
コンバータのスリップを減少して燃費を向上させ、また
このスリップによりエンジンからのトルク変動を緩和す
る作用を有するもの′ｔ７ある。In FIG. 7, a torque converter q equipped with a friction clutch 2 used in an automatic transmission for an automobile is shown, and the friction clutch 2 is a slip type clutch that transmits power while constantly slipping. , when the clutch is engaged, the power from the multi-rank shaft 6 of the engine is mainly transmitted to the output shaft g via the clutch, and part of the power is transmitted via the torque converter lI'l, so that the torque converter slips. There is a type 't7 which has the function of reducing the amount of slippage and improving fuel efficiency, and also has the effect of alleviating torque fluctuations from the engine due to this slip.
摩擦クラッチコとトルクコンバータ１Ｉｔｄ一体内に形
成されており、クランク軸乙に固着されたドライブプレ
ートｉｏ、同ドライブプレートに固着ると共に出力軸Ｓ
にスプライン嵌合されて同出方軸と一体に回転すゐター
ビン／ｑ、ハウジング／ｌに一方向りラッチ／ｇｆ介し
て支持さ紅たステータ、２０１タービン／ｌのシェル２
２に固着されたトランスファリング２ダを介してタービ
ンと一体に（ロ）転できるＬうに連結されると共に出方
軸ＳにＱＬ軸方向に摺動自在に配置されたピストンλｔ
１及ヒ同ピストンの外周部に対向した位置においてポン
プノコのシェル、２ｇと結合されたカバー３０に固着さ
れているクラッチフェーシング３２を有しており、ピス
トン２１とカバー３０との間には油田室３ｑが形成され
、タービン／ｑのシェル２２とピストンλｔとの間には
油圧室３６が形成されている。A friction clutch and a torque converter 1Itd are formed in one body, and a drive plate io is fixed to the crankshaft O, and an output shaft S is fixed to the drive plate.
Turbine/q is spline-fitted to rotate integrally with the same output shaft, stator is supported via a one-way latch/gf to housing/l, shell 2 of 201 turbine/l
A piston λt is connected to the turbine through a transfer ring 2 which is fixed to the turbine 2, and is arranged to be slidable in the direction of the QL axis on the output shaft S.
A clutch facing 32 is fixed to a cover 30 connected to a pump saw shell 2g at a position facing the outer circumference of the piston 1 and 2, and an oil well chamber is provided between the piston 21 and the cover 30. 3q is formed, and a hydraulic chamber 36 is formed between the shell 22 of the turbine/q and the piston λt.
上記摩擦クラッチλ及びトルクコンバータダへの圧油の
供給は油圧制御装瞳（図示しない）にＬつて制御される
。圧油が、矢印で示すように、出力軸Ｓに外嵌されたポ
ンプノコのスリーブ３１１（７）内面に形成された油路
ｅｏ及びトルクコンバータダの内部を通って油ＦＥ寥ａ
ｔ、に導びかれ、さらに７エーシング３．２とピストン
コ乙間の隙間、油圧室３ダそして出力軸８に穿設された
油路ｑコを通って排出される時、ピストン、２ｔが左方
に移動されて摩擦クラッチλが係合され、圧油が逆方□
向に循環される時、ピストンが右方に移動されて摩擦り
、ラッチが離脱される。The supply of pressure oil to the friction clutch λ and the torque converter is controlled by a hydraulic control system (not shown). Pressure oil passes through the oil passage eo formed on the inner surface of the sleeve 311 (7) of the pump saw fitted on the output shaft S and the inside of the torque converter, as shown by the arrow, to the oil FE pipe a.
When the piston 2t is guided to the left side and discharged through the gap between the 7 acing 3.2 and the piston shaft 2, the hydraulic chamber 3da, and the oil passage q drilled in the output shaft 8, the piston 2t is guided to the left side. The friction clutch λ is engaged, and the pressure oil is moved in the opposite direction □
When cycled in the opposite direction, the piston is moved to the right and rubs, causing the latch to disengage.
第２図に拡大して示すように、ピストン２６は、タービ
ン／４（に固着されたトランスファリング評にスプライ
ン等にＬつ・て連結されてタービンと一体に回転すると
共に、カバー３０に固着されたフェーシング３コと摩擦
接触する環状の７工−シング押付部材ｔｉｙ及び出力軸
８に対し摺動自在に配置されると共に、Ｏリングシール
ＩｉＺ Ａ［ｊ：つてフェーシング押付部材ｔダと密封
的に接触する油圧量は部材ｌＩ＆で構成されている。As shown in an enlarged view in FIG. 2, the piston 26 is connected to a transfer ring fixed to the turbine 4 by a spline or the like and rotates together with the turbine, and is fixed to the cover 30. The annular seven-singing pressing member tiy that comes into frictional contact with the three facings and the output shaft 8 is slidably arranged, and the O-ring seal IiZ A [j: The O-ring seal IiZ A[j: The facing pressing member tda The contacting hydraulic quantity is constituted by the member lI&.
第２図に示す本発明の第１実施例において、）エーシン
グ押付部材ｕｌＩＩｎ油圧受は部材ダｇの外周に設けら
れたインロー！；ＯＫＬり摺動自在に支持されている。In the first embodiment of the present invention shown in FIG. 2, the acing pressing member ulIIn hydraulic pressure receiver is a spigot provided on the outer periphery of the member dag. ; OKL is slidably supported.
油圧量は部材ｑｇｆ′ｉ、丸みを有する凸状の神田部Ｓ
コを具え、この押圧面はフェーシング押付部材１１Ｑの
丸みを有する受圧部ＳＯと当接する。この押圧面Ｓλと
受千部Ｓｔｔとの当接点は７エーシング３２の押圧中心
と一致するＬうに設けられている。The hydraulic pressure is determined by the member qgf'i, the rounded convex Kanda section S
This pressing surface contacts the rounded pressure receiving portion SO of the facing pressing member 11Q. The contact point between this pressing surface Sλ and the receiving part Stt is provided at a position L that coincides with the pressing center of the seven acing 32.
第３図に示す本発明の第コ実施例において、フェーシン
グ押付部材ダダに゛インローＳＯが設けられ、これに：
り同押付部材が油圧量は部材ｌＩｇに摺動自在に支持さ
れている。油圧量は部材ｙｇはフェーシング押付部材ｌ
Ｉｑの平坦面と当接する平坦な押圧面ｓｔ’＞具え、上
記平坦面と押圧面Ｓｔとの当接中心はフェーシング３２
の押圧中心と一致するＬうに設けられている。In the fourth embodiment of the present invention shown in FIG. 3, a spigot SO is provided on the facing pressing member, and this:
The pressing member is slidably supported by the member lIg under hydraulic pressure. The hydraulic pressure is the member yg and the facing pressing member l.
A flat pressing surface st' that comes into contact with the flat surface of Iq is provided, and the center of contact between the flat surface and the pressing surface St is facing 32
It is provided in L which coincides with the center of pressure.
第４図に示す本発明の第３実施例において、第２実施例
と同様に設けられたインローＳＯに！す７工−シング押
付部材Ｑ’ｌが油圧量は部材ｌ１ｇに支持されている。In the third embodiment of the present invention shown in FIG. 4, the spigot SO is provided in the same manner as in the second embodiment! The pressing member Q'l is hydraulically supported by the member l1g.
油圧量は部材ｙｇは第１実施例と同様な丸みを有する凸
状の押−圧部Ｓ２を具え、この押圧面はフェーシング押
付部材ＩＱの平坦面と当接し、この当接点はフェーシン
グ３コの押圧中心と一致している。The hydraulic pressure is determined by the member yg, which has a convex pressing portion S2 with a roundness similar to that of the first embodiment, and this pressing surface contacts the flat surface of the facing pressing member IQ, and this contact point is located on the three facings. It matches the center of pressure.
上述した本発明の構成にＬれば、摩擦クラッチのピスト
ンコ乙ヲフエーシング押付部材＜＜ ＜’ ト油田受は
部材ｅｇの一つの分割した部材で構成し、且つこのλつ
の部材の当接中心とフェーシング３２の押子中心とを一
致させるようにしているので、り、ラッチ保合時フェー
シングと７工−シング押付部材とは均一に摩擦接触し、
片当りにＬり生じるクラッチのトルク容量の低下、クラ
ッチの偏摩耗、タラツチジャターーの発生等を効果的に
防止できるものである。According to the above-mentioned structure of the present invention, the piston of the friction clutch and the facing pressing member <<<' and the oil field bridge are composed of one divided member of the member eg, and the center of contact of these λ members and the facing are Since the center of the pusher 32 is aligned with the center of the pusher 7, the facing and the pressing member 7 come into uniform frictional contact when the latch is engaged.
This effectively prevents a reduction in the torque capacity of the clutch, uneven wear of the clutch, and the occurrence of sluggish jitter caused by uneven contact.
上記各実施例においては、インロー！；ＯＫＫって７工
−シング押付部材ダダを油圧量は部材ｑ 、ｇに摺動自
在に支持しているが、タービン／９に固着されたト？ン
スファリング２ｑとフェーシング押付部材９４とのスプ
ライン部の内径を等しくすることにＬす、同押付部材を
タービンに対して支持させるＬうにしてもＬい。In each of the above embodiments, the spigot! OKK is a 7-engine pressing member Dada that is slidably supported by hydraulic pressure members q and g, but is it fixed to the turbine /9? In addition to making the inner diameters of the spline portions of the facing pressing member 94 equal to the inner diameters of the spline portions of the facing pressing member 94, it is also possible to support the pressing member with respect to the turbine.
第１図は本発明にＬる摩擦クラッチとトルクコンバータ
の断面図、第２図は本発明の第７実施例を示す摩擦クラ
ッチの要部拡大断面図、第３図は本発明の第コ実施例を
示す第２図と同様な断面図。
第９図は本発明の第３実施例を示す第２図と同様な断面
図である。
２書・摩擦クラッチ、ｑ・・トルクコンバータ、１２・
・ポンプ、ｌｌＩ・・タービン、２０・・スデータ、コ
ダ・Φトランスファリング、ゝ２１・・ピストン、３０
・・カバー、３コ・・クラッチフェーシング、ｑｌＩ・
・７エーシン’ｊ 押付部材、ｌＩｔ。
・・０リングシール、＆＆・・油圧量は部材、５２・・
押圧部、！４・・押圧面。FIG. 1 is a cross-sectional view of a friction clutch and a torque converter according to the present invention, FIG. 2 is an enlarged cross-sectional view of the main part of a friction clutch showing a seventh embodiment of the present invention, and FIG. FIG. 2 is a cross-sectional view similar to FIG. 2 illustrating an example; FIG. 9 is a sectional view similar to FIG. 2 showing a third embodiment of the present invention. Book 2・Friction clutch, q・torque converter, 12・
・Pump, llI...Turbine, 20...Stater, Koda Φ Transferring, ゝ21...Piston, 30
・・Cover, 3 pieces・・Clutch facing, qlI・
・7Ashin'j Pressing member, lIt.・・0-ring seal, &＆・hydraulic pressure is a member, 52...
Pressing part! 4... Pressing surface.
Claims (1)
田作動のピストンを有する摩擦クラッチにおいて、上記
ピストンが上記クラッチフェーシングを押付けるフェー
シング押付部材及び同押付部材と密封的に接触する油圧
骨は部材で構成され、上記油圧骨は部材に当接する上記
７工−シング押付部材の押圧部分と上記クラッチフェー
シングの押棺中心とを一致させるＬうにしたこと孕特徴
とする摩擦クラッチ。7. In a friction clutch having an oilfield-operated piston that presses a clutch facing and an acing, a facing pressing member with which the piston presses the clutch facing and a hydraulic bone that makes sealing contact with the pressing member are composed of members, and the above-mentioned The friction clutch is characterized in that the hydraulic rib is designed to align the pressing portion of the pressing member that contacts the member with the center of the pressing member of the clutch facing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12833081A JPS5830531A (en) | 1981-08-17 | 1981-08-17 | Friction clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12833081A JPS5830531A (en) | 1981-08-17 | 1981-08-17 | Friction clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5830531A true JPS5830531A (en) | 1983-02-23 |
Family
ID=14982114
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12833081A Pending JPS5830531A (en) | 1981-08-17 | 1981-08-17 | Friction clutch |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5830531A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2765938A1 (en) * | 1997-08-26 | 1999-01-15 | Luk Getriebe Systeme Gmbh | Hydrodynamic torque converter |
| EP2149726A1 (en) * | 2008-07-31 | 2010-02-03 | Valeo Embrayages | Lock-up clutch for a hydrokinetic coupling device comprising improved linking means |
| KR101055839B1 (en) | 2009-11-23 | 2011-08-09 | 현대자동차주식회사 | Torque converter of car |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5754767A (en) * | 1980-09-16 | 1982-04-01 | Aisin Warner Ltd | Lockup torque converter |
-
1981
- 1981-08-17 JP JP12833081A patent/JPS5830531A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5754767A (en) * | 1980-09-16 | 1982-04-01 | Aisin Warner Ltd | Lockup torque converter |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2765938A1 (en) * | 1997-08-26 | 1999-01-15 | Luk Getriebe Systeme Gmbh | Hydrodynamic torque converter |
| WO1999010663A1 (en) * | 1997-08-26 | 1999-03-04 | Luk Getriebe-Systeme Gmbh | Hydrodynamic torque converter |
| DE19881219B4 (en) * | 1997-08-26 | 2011-12-01 | Schaeffler Technologies Gmbh & Co. Kg | Hydrodynamic torque converter |
| EP2149726A1 (en) * | 2008-07-31 | 2010-02-03 | Valeo Embrayages | Lock-up clutch for a hydrokinetic coupling device comprising improved linking means |
| FR2934660A1 (en) * | 2008-07-31 | 2010-02-05 | Valeo Embrayages | LOCKING CLUTCH FOR A HYDROKINETIC COUPLING APPARATUS HAVING IMPROVED BONDING MEANS. |
| JP2010048414A (en) * | 2008-07-31 | 2010-03-04 | Valeo Embrayages | Lock-up clutch for hydrokinetic coupling device including improved connection means |
| US8276723B2 (en) | 2008-07-31 | 2012-10-02 | Valeo Embrayages | Lock-up clutch for hydrokinetic coupling device including improved connection means |
| KR101055839B1 (en) | 2009-11-23 | 2011-08-09 | 현대자동차주식회사 | Torque converter of car |
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