JPS6128129Y2 - - Google Patents
Info
- Publication number
- JPS6128129Y2 JPS6128129Y2 JP17561282U JP17561282U JPS6128129Y2 JP S6128129 Y2 JPS6128129 Y2 JP S6128129Y2 JP 17561282 U JP17561282 U JP 17561282U JP 17561282 U JP17561282 U JP 17561282U JP S6128129 Y2 JPS6128129 Y2 JP S6128129Y2
- Authority
- JP
- Japan
- Prior art keywords
- clutch plate
- valve
- turbine wheel
- communication hole
- input case
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000012530 fluid Substances 0.000 claims description 25
- 238000004891 communication Methods 0.000 claims description 24
- 238000006073 displacement reaction Methods 0.000 description 14
- 230000005540 biological transmission Effects 0.000 description 5
- 230000008602 contraction Effects 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 239000002783 friction material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Control Of Fluid Gearings (AREA)
Description
【考案の詳細な説明】
本考案は、主として車両用変速機に用いられる
流体トルクコンバータ用クラツチの作動制御装置
に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an actuation control device for a clutch for a fluid torque converter mainly used in a vehicle transmission.
従来、この種流体トルクコンバータ用クラツチ
として、例えばUSP4240532号明細書により、エ
ンジンに連結される一側の入力ケースと該入力ケ
ースに連結される他側のポンプ翼車とで囲われる
流体トルクコンバータ本体の内部空隙に、車両の
駆動輪に連る出力軸に連結されるタービン翼車
と、該タービン翼車と該入力ケースとの間のクラ
ツチ板とを設け、該クラツチ板を軸方向に移動自
在としてその両側面に作用させる流体圧力差に応
じて該入力ケースに係脱自在とすると共に、該ク
ラツチ板と該タービン翼車とをダンパスプリング
を介して相対回転可能に連結し、高速巡航時等に
おいて該クラツチ板を該入力ケースに係合させ
て、入力軸→入力ケース→クラツチ板→ダンパス
プリング→タービン翼車→出力軸の系路での機械
的トルク伝達により流体トルクコンバータでの滑
りを防止した効率的なトルク伝達を行い得られる
ようにし、且つトルク変動を該ダンパスプリング
の伸縮動作で吸収して、入出力軸間のトルク変動
の伝達を阻止し得るようにしたものは知られる
が、このものではエンジンの駆動トルクの小さな
領域でのトルク変動を吸収しにくい不都合を伴
う。 Conventionally, as a clutch for this type of fluid torque converter, for example, according to US Pat. A turbine wheel connected to an output shaft connected to a drive wheel of the vehicle and a clutch plate between the turbine wheel and the input case are provided in the internal gap of the vehicle, and the clutch plate is movable in the axial direction. The clutch plate can be freely engaged and disengaged from the input case according to the fluid pressure difference applied to both sides of the input case, and the clutch plate and the turbine impeller are connected through a damper spring so that they can rotate relative to each other. At this time, the clutch plate is engaged with the input case to prevent slippage in the fluid torque converter by mechanical torque transmission in the input shaft → input case → clutch plate → damper spring → turbine wheel → output shaft system. It is known that the damper spring is capable of efficiently transmitting torque, absorbing torque fluctuations through the expansion and contraction of the damper spring, and preventing the transmission of torque fluctuations between the input and output shafts. This method has the disadvantage that it is difficult to absorb torque fluctuations in a region where the driving torque of the engine is small.
これを詳述するに、ダンパスプリングは駆動ト
ルクの大きな領域でのトルク変動を吸収し得るよ
うそのばね定数を比較的高く設定するもので、駆
動トルクの小さな領域でのトルク変動に対して
は、定常トルクに対するトルク変動巾の割合が大
きくなるにもかかわらず、該スプリングにこれに
対応した充分な伸縮動作が与えられず、トルク変
動を吸収しにくくなるのである。 To explain this in detail, the damper spring has a relatively high spring constant so as to be able to absorb torque fluctuations in a region where the driving torque is large, and to absorb torque fluctuations in a region where the driving torque is small. Even though the ratio of the torque fluctuation width to the steady torque increases, the spring is not given sufficient expansion/contraction action to correspond to this, making it difficult to absorb torque fluctuations.
そこで本願出願人は、先にかかる不都合を解消
すべく、特願昭57−107675号によりクラツチ板
に、その両側面間を連通する連通孔と、該連通孔
を開閉する開閉弁とを設け、該開閉弁をタービン
翼車のクラツチ板に対する逆転方向への相対回転
で閉じ側に動作させるようにした流体トルクコン
バータ用クラツチの作動制御装置を提案した。 Therefore, in order to eliminate the above-mentioned inconvenience, the applicant of the present application, in accordance with Japanese Patent Application No. 57-107675, provided a communication hole that communicates between both sides of the clutch plate, and an on-off valve that opens and closes the communication hole. We have proposed an operation control device for a clutch for a fluid torque converter in which the opening/closing valve is operated toward the closing side by relative rotation in the reverse direction with respect to the clutch plate of the turbine impeller.
これによれば、該タービン翼車の該クラツチ板
に対する逆転方向への相対回転変位置の小さな駆
動トルクの小さな領域では、該連通孔が開かれて
そこからの流体リークにより、該クラツチ板の両
側面間の流体圧力差が減少され、該クラツチ板の
係合力が弱められてその滑りを生じ易くなり、か
くて駆動トルクの小さな領域でのトルク変動は該
クラツチ板の滑りで効果的に吸収される。 According to this, in a region where the drive torque is small and the relative rotational displacement position of the turbine impeller in the reverse direction with respect to the clutch plate is small, the communication hole is opened and fluid leaks from the communication hole, causing fluid leakage from both sides of the clutch plate. The fluid pressure difference between the surfaces is reduced, and the engagement force of the clutch plate is weakened, making it more likely to slip, so that torque fluctuations in the small region of driving torque can be effectively absorbed by the clutch plate slipping. Ru.
然し、このもので該開閉弁は、該クラツチ板上
に該タービン翼車の相対回転でこれと一体に周方
向に摺動されるように設けた摺動部材で構成され
るを一般としたもので、これによれば駆動トルク
に対する該開閉弁の変位量が一義的に定まり、こ
の場合該開閉弁による該連通孔の開閉切換を生ず
る駆動トルクの大きさは該連通孔の形成位置を変
えることで適宜に設定出来るが、該連通孔の開度
を必要に応じ、例えば駆動トルクの比較的小さな
限定された領域で増減制御したり、或いは逆に駆
動トルクの広範囲な領域に亘つて増減制御すると
いつた開度制御の設定は該連通孔の形成位置の変
更では対処出来ず、クラツチ板の係合力を駆動ト
ルクに応じてより細かく制御し得るようにするに
は該開閉弁の駆動トルクに対する変位置を設計上
変更し得るようにすることが望まれる。 However, in this case, the on-off valve is generally composed of a sliding member provided on the clutch plate so as to slide integrally with the turbine wheel in the circumferential direction due to the relative rotation of the turbine wheel. According to this, the amount of displacement of the on-off valve relative to the driving torque is uniquely determined, and in this case, the magnitude of the driving torque that causes the on-off valve to switch the communication hole to open or close can be determined by changing the formation position of the communication hole. However, the opening degree of the communication hole can be adjusted as necessary, for example, by increasing or decreasing the opening degree in a limited area where the driving torque is relatively small, or conversely, by controlling the opening degree over a wide range of driving torque. The setting of the opening control cannot be handled by changing the formation position of the communication hole, and in order to more precisely control the engagement force of the clutch plate according to the driving torque, it is necessary to change the driving torque of the opening/closing valve. It is desirable to be able to change the position in design.
本考案は、かかる要望を満す装置を提供するこ
とをその目的とするもので、入力軸に連結される
一側の入力ケースと該入力ケースに連結される他
側のポンプ翼車とで囲われる流体トルクコンバー
タ本体の内部空隙に、出力軸に連結されるタービ
ン翼車と、該タービン翼車と該入力ケースとの間
のクラツチ板とを設け、該クラツチ板を軸方向に
移動自在としてその両側面に作用させる流体圧力
差に応じて該入力ケースに係脱自在とすると共
に、該クラツチ板と該タービン翼車とをダンパス
プリングを介して相対回転可能に連結し、該クラ
ツチ板に、その両側面間を連通する連通孔と、該
連通孔を開閉する開閉弁とを設けて、該開閉弁を
該タービン翼車の該クラツチ板に対する逆転方向
への相対回転で閉じ側に動作させるようにしたも
のにおいて、該開閉弁を該クラツチ板に枢着され
る揺動部材で構成し、該揺動部材にその枢軸から
の距離を適宜に設定して、該連通孔を開閉する弁
部と、該タービン翼車の該相対回転で該揺動部材
を揺動させる該タービン翼車との連結部とを備え
たことを特徴とする。 The purpose of the present invention is to provide a device that satisfies such demands, and is surrounded by an input case on one side connected to an input shaft and a pump impeller on the other side connected to the input case. A turbine wheel connected to the output shaft and a clutch plate between the turbine wheel and the input case are provided in the internal gap of the fluid torque converter main body, and the clutch plate is movable in the axial direction. The input case can be freely engaged and disengaged according to a fluid pressure difference applied to both side surfaces, and the clutch plate and the turbine wheel are relatively rotatably connected via a damper spring. A communication hole that communicates between both side surfaces and an on-off valve that opens and closes the communication hole are provided, and the on-off valve is moved to the closing side by relative rotation of the turbine impeller in a reverse direction with respect to the clutch plate. In the above-mentioned device, the opening/closing valve is constituted by a swinging member pivotally attached to the clutch plate, and a valve portion that opens and closes the communication hole by appropriately setting a distance from the pivot to the swinging member; The present invention is characterized in that it includes a connecting portion with the turbine wheel that swings the swinging member by the relative rotation of the turbine wheel.
次いで本考案を図示の実施例に付説明する。 Next, the present invention will be explained with reference to the illustrated embodiments.
図面で１は同一軸線上の前後にエンジンに連る
入力軸２と車両の駆動輪その他の負荷に連る出力
軸３とを有する流体トルクコンバータ本体を示
し、該本体１は、該入力軸２に連る前側の入力ケ
ース４と、該入力ケース４に連結される後側のポ
ンプ翼車５とを備えると共に該入力ケース４と該
ポンプ翼車５とで囲われる内部空隙６に、該出力
軸３に連結されるタービン翼車７と、該タービン
翼車７と該ポンプ翼車５との間のステータ翼車８
とを備えて、該入力軸２の回転によればこれら翼
車５，７，８間に内部流体が循環されて該出力軸
３への流体トルク伝達が与えられるように構成さ
れ、更に該タービン翼車７と該入力ケース４との
間に軸方向に移動自在在のクラツチ板９を備え
て、これをその前後両側面に作用する流体圧力差
に応じて該入力ケース４に係脱自在とし、ここで
該クラツチ板９はダンパスプリング１０を介して
該タービン翼車７に連結されて該タービン翼車７
において該出力軸３に連結されるものとし、かく
て該クラツチ板９の該入力ケース４への係合によ
れば、入力軸２→入力ケース４→クラツチ板９→
ダンパスプリング１０→タービン翼車７→出力軸
３の系路での機械的トルク伝達が与えられるよう
にした。 In the drawings, reference numeral 1 denotes a fluid torque converter main body having an input shaft 2 connected to the engine and an output shaft 3 connected to the drive wheels and other loads of the vehicle on the same axis at the front and rear. The output is provided in an internal space 6 surrounded by the input case 4 and the pump impeller 5, and includes a front input case 4 connected to the input case 4 and a rear pump impeller 5 connected to the input case 4. a turbine wheel 7 connected to the shaft 3; a stator wheel 8 between the turbine wheel 7 and the pump wheel 5;
The rotation of the input shaft 2 circulates internal fluid between the impellers 5, 7, and 8 to provide fluid torque transmission to the output shaft 3, and the turbine A clutch plate 9 that is movable in the axial direction is provided between the impeller 7 and the input case 4, and can be freely engaged and disengaged from the input case 4 according to the fluid pressure difference acting on both front and rear sides of the clutch plate 9. , here, the clutch plate 9 is connected to the turbine wheel 7 via a damper spring 10, and the clutch plate 9 is connected to the turbine wheel 7 via a damper spring 10.
According to the engagement of the clutch plate 9 with the input case 4, the input shaft 2→input case 4→clutch plate 9→
Mechanical torque transmission is provided through the damper spring 10→turbine wheel 7→output shaft 3 system.
これを図示のものに付更に詳述するに、該クラ
ツチ板９は、その後側面に内部空隙６内の流体圧
と、その前側面にこれと該入力ケース４との間隙
１１内の流体圧とを作用させて、該間隙１１内の
流体圧をこれに該出力軸３の軸孔１２を介して連
る流体圧制御装置（図示せず）で減圧することに
より前進作動され、外周部前面の摩擦材１３にお
いて、該入力ケース４に摩擦係合されるものと
し、又該ダンパスプリング１０は、第２図及び第
３図に示す如く該クラツチ板９の外周部後面の環
状の凹部９ａ内に互に周方向の間隙を存して収容
した各コイルスプリングで構成されるものとし、
該クラツチ板９に該各スプリング１０毎にこれを
内方に抜止めする支持片１４を取付けて、該支持
片１４に該各スプリング１０をその両端面のスプ
リングワツシヤ１０ａ，１０a′を介して挾持する
両端の入力側リテーナ１５，１５を突設し、更に
該各スプリング１０の配置間隙に該タービン翼車
７側からのびる出力側リテーナ１６を挿入した。
図面で９ｂは該各スプリング１０の伸縮動作を円
滑にすべく該凹部９ａ内に設けたガイド板を示
す。 In addition to what is shown in the drawings, to explain this in more detail, the clutch plate 9 has a rear side surface that receives the fluid pressure in the internal space 6, and a front surface that stores the fluid pressure in the gap 11 between the clutch plate 9 and the input case 4. is applied, and the fluid pressure in the gap 11 is reduced by a fluid pressure control device (not shown) connected through the shaft hole 12 of the output shaft 3, whereby the forward movement is performed. The friction material 13 is frictionally engaged with the input case 4, and the damper spring 10 is fitted into an annular recess 9a on the rear surface of the outer periphery of the clutch plate 9, as shown in FIGS. It shall be composed of coil springs housed with circumferential gaps between each other,
A support piece 14 is attached to the clutch plate 9 to prevent each spring 10 from coming out inwardly, and each spring 10 is attached to the support piece 14 through spring washers 10a, 10a' on both end faces thereof. Input side retainers 15, 15 at both ends to be clamped are provided in a protruding manner, and an output side retainer 16 extending from the turbine wheel 7 side is inserted into a gap between the springs 10.
In the drawings, reference numeral 9b indicates a guide plate provided within the recess 9a to facilitate the expansion and contraction of each spring 10.
ここでエンジンの駆動回転方向即ち正転方向を
第２図で時計方向とすると、エンジンからの駆動
トルクの伝達時、該タービン翼車７は該クラツチ
板９に対し逆転方向即ち反時計方向への相対回転
を生ずる。この場合該各スプリング１０は、該出
力側リテーナ１６を介して駆動トルクに応じた弾
力が発生される迄の圧縮変形を与えられるもの
で、かくて該タービン翼車７の反時計方向への相
対回転変位置は駆動トルクに応じて大きくなる。 Here, assuming that the driving rotation direction of the engine, that is, the forward rotation direction, is clockwise in FIG. Causes relative rotation. In this case, each spring 10 is compressed and deformed through the output side retainer 16 until elasticity is generated in accordance with the driving torque, and thus the relative rotation of the turbine wheel 7 in the counterclockwise direction is applied. The rotational displacement position increases according to the driving torque.
該各スプリング１０は、トルク変動に際し、駆
動トルクに応じた所定の圧縮変位位置を中心にし
た伸縮動作でトルク変動を吸収すべく作動するも
ので、この場合該各スプリング１０は、駆動トル
クの大きな領域においてこれが定常状態で最大圧
縮位置に圧縮変位されて以後のトルク変動を吸収
し得なくなることのないよう比較的ばね定数の高
いものを用いるため、駆動トルクの小さな領域で
はトルク変動を充分に吸収し得なくなる。 Each spring 10 operates to absorb the torque fluctuation by expanding and contracting around a predetermined compression displacement position according to the driving torque when the torque fluctuates. In order to prevent this from compressing to the maximum compression position in a steady state and being unable to absorb subsequent torque fluctuations, a spring with a relatively high constant is used, so torque fluctuations can be sufficiently absorbed in regions where the drive torque is small. It becomes impossible.
そこで、該クラツチ板９に、第１図及び第２図
に示す如くその両側面間を連通する連通孔１７
と、該連通孔１７を開閉する開閉弁１８とを設け
て、該開閉弁１８を該タービン翼車７の該クラツ
チ板９に対する逆転方向即ち反時計方向への相対
回転で閉じ側に動作させるようにし、この相対回
転変位量の小さな駆動トルクの小さな領域では、
該連通孔１７が開かれて該連通孔１７を介しての
流体リークにより該クラツチ板９の両側面に作用
する流体圧力差が減少され、該クラツチ板９の該
入力ケース４への係合力が弱められるようにし、
かくてかかる領域でのトルク変動を該クラツチ板
９の滑りで効果的に吸収し得るようにする。 Therefore, a communication hole 17 is provided in the clutch plate 9, which communicates between both sides of the clutch plate 9, as shown in FIGS. 1 and 2.
and an on-off valve 18 for opening and closing the communication hole 17, so that the on-off valve 18 is moved toward the closing side by relative rotation of the turbine wheel 7 in the reverse direction with respect to the clutch plate 9, that is, in the counterclockwise direction. In this small region of small driving torque with small relative rotational displacement,
When the communication hole 17 is opened, the fluid leakage through the communication hole 17 reduces the fluid pressure difference acting on both sides of the clutch plate 9, and the engagement force of the clutch plate 9 with the input case 4 is reduced. to be weakened;
Thus, torque fluctuations in this region can be effectively absorbed by the slippage of the clutch plate 9.
以上は上記した先の提案のものと特に異らない
が、本考案によれば、該開閉弁１８を該クラツチ
板９に枢着される揺動部材１９で構成し、該揺動
部材１９に、その枢軸２０からの距離を適宜に設
定して該連通孔１７を開閉する弁部２１と、該タ
ービン翼車７の逆転方向即ち反時計方向への相対
回転で該揺動部材１９を揺動させる該タービン翼
車７との連結部２２とを備えた。 Although the above is not particularly different from the above-mentioned proposal, according to the present invention, the on-off valve 18 is constituted by a swinging member 19 pivotally connected to the clutch plate 9. , a valve part 21 that opens and closes the communication hole 17 by appropriately setting the distance from the pivot shaft 20, and a valve part 21 that swings the swinging member 19 by relative rotation of the turbine impeller 7 in the reverse direction, that is, in the counterclockwise direction. A connecting portion 22 with the turbine impeller 7 is provided.
図示のものでは、該揺動部材１９を、該枢軸２
０から径方向にのびる板片で構成し、これに径方
向内方に延びる適当な長さの弾性片１９ａをリベ
ツト２３止めし、該弾性片１９ａの内端部を該ク
ラツチ板９上に弾接させて該内端部により該弁部
２１を構成し、該弁部２１による該連通孔１７の
シール性を高めた。 In the illustrated example, the swinging member 19 is connected to the pivot shaft 2.
An elastic piece 19a of an appropriate length extending inwardly in the radial direction is fixed with a rivet 23 to this plate piece, and the inner end of the elastic piece 19a is elastically attached to the clutch plate 9. The valve portion 21 is formed by the inner end portions in contact with each other, and the sealing performance of the communication hole 17 by the valve portion 21 is improved.
該連結部２２は、該揺動部材１９の外端側の適
当な位置に植設したピンで構成されるもので、こ
れを何れかのダンパスプリング１０の配置位置の
反時計方向側に位置させ、該タービン翼車７の反
時計方向への相対回転でこれに設けた出力側リテ
ーナ１６が当接する該スプリング１０の時計方向
の端面のスプリングワツシヤ１０ａに反時計方向
にのびる連杆としてのピアノ線２４を固設して、
該連杆２４の先端を該連結部２２に連結した。 The connecting portion 22 is composed of a pin implanted at an appropriate position on the outer end side of the swinging member 19, and is positioned counterclockwise from the position where one of the damper springs 10 is disposed. , a piano as a continuous rod extending counterclockwise to a spring washer 10a on the clockwise end surface of the spring 10, which comes into contact with the output side retainer 16 provided on the turbine impeller 7 as it rotates counterclockwise. Fix the line 24,
The tip of the connecting rod 24 was connected to the connecting portion 22.
尚、該ピアノ線２４は、該スプリング１０の反
時計方向の端面のスプリングワツシヤ１０a′と更
にガイド部材２５とに挿通して、これらにガイド
されて周方向に移動されるようにし、又該ピアノ
線２４は該連結部２２を構成するピンに軸方向に
移動自在に巻止めし、該スプリング１０やワツシ
ヤ１０ａが該クラツチ板９から浮動してもその動
きが該揺動部材１９に伝わらないようにした。図
面で２２ａはピアノ線２４を抜止めすべく該連結
部２２に設けた抜止め片を示す。次いでその作動
を説明するに、クラツチ板９の係合時、タービン
翼車７は該クラツチ板９に対し、駆動トルクに応
じた反時計方向への相対回転を生ずるもので、こ
れによれば出力側リテーナ１６とスプリングワツ
シヤ１０ａとピアノ線２４とを介して揺動部材１
９の連結部２２が上記の如く該タービン翼車７の
相対回転変位量に応じた変位置で反時計方向に押
動され、該揺動部材１９の枢軸２０を中心とした
反時計方向への揺動を生じて、弁部２１に連通孔
１７を閉じる方向への揺動変位が与えられるが、
該タービン翼車７の相対回転変位量従つて駆動ト
ルクの大きさと該弁部２１の変位量との関係は、
該枢軸２０からの該弁部２１と該連結部２２との
距離l1，l2の比l1／l2で定まり、l1／l2＞１とする
と、該タービン翼車７の変位置よりも該弁部２１
の変位量の方が大きくなり、駆動トルクの比較的
小さな限定された領域で該弁部２１を第２図にＡ
で示す閉じ始めの位置から仝図にＢで示す全閉位
置との間に変位させて該連通孔１７の開度を増減
制御して、該クラツチ板９の係合力をかかる領域
で細かく制御することが可能となり、又l1／l2＜
１とすると、該タービン翼車７の変位量よりも該
弁部２１の変位量の方が少さくなり、駆動トルク
の中程度の領域から大きな領域までの広範囲な領
域に亘つて該連通孔１７の開度を増減制御出来、
該クラツチ板９の係合力が駆動トルクに応じた広
範囲に制御することが可能となる。 The piano wire 24 is inserted through the spring washer 10a' on the counterclockwise end face of the spring 10 and further through the guide member 25 so that it is guided by these and moved in the circumferential direction. The piano wire 24 is wound around the pin constituting the connecting portion 22 so as to be movable in the axial direction, so that even if the spring 10 or the washer 10a floats from the clutch plate 9, the movement will not be transmitted to the swinging member 19. I did it like that. In the drawings, reference numeral 22a indicates a retaining piece provided on the connecting portion 22 to prevent the piano wire 24 from being pulled out. Next, to explain its operation, when the clutch plate 9 is engaged, the turbine impeller 7 generates a relative rotation in the counterclockwise direction with respect to the clutch plate 9 according to the driving torque, and according to this, the output The swinging member 1 is connected to the side retainer 16, the spring washer 10a, and the piano wire 24.
As described above, the connecting portion 22 of the oscillating member 19 is pushed counterclockwise at a position corresponding to the relative rotational displacement of the turbine impeller 7, and is moved counterclockwise around the pivot shaft 20 of the swinging member 19. This causes rocking, and a rocking displacement is given to the valve portion 21 in the direction of closing the communication hole 17;
The relationship between the relative rotational displacement of the turbine wheel 7, that is, the magnitude of the driving torque, and the displacement of the valve portion 21 is as follows:
The distances l 1 and l 2 between the valve portion 21 and the connecting portion 22 from the pivot shaft 20 are determined by the ratio l 1 /l 2 , and if l 1 / l 2 > 1, the position of the turbine blade wheel 7 is than the valve part 21
The amount of displacement becomes larger, and in a limited area where the driving torque is relatively small, the valve portion 21 is moved as shown in FIG.
The opening degree of the communication hole 17 is controlled to increase or decrease by displacing it between the initial closing position shown by B and the fully closed position shown by B in the figure, and the engagement force of the clutch plate 9 is finely controlled in this area. This makes it possible, and l 1 /l 2 <
1, the amount of displacement of the valve portion 21 is smaller than the amount of displacement of the turbine impeller 7, and the communication hole 17 is larger than the amount of displacement of the turbine impeller 7 over a wide range from a medium range to a large drive torque range. The opening degree can be increased or decreased,
The engagement force of the clutch plate 9 can be controlled over a wide range depending on the driving torque.
尚、揺動部材１９は流体トルクコンバータの軸
心に対し偏心位置で揺動されるため、その揺動で
連結部２２のクラツチ板９やタービン翼車７に対
する径方向位置が変化し、該タービン翼車７の変
位量が増加すると、該連結部２２の径方向位置が
内方にずれてピアノ線２４の彎曲度が増し、その
応力疲労や、又該ピアノ線２４を介して作用され
る径方向外方への応力により連結部２２や枢軸２
０の偏摩耗等が懸念されるため、第４図に示す如
くピアノ線２４の中間に関節点２４ａを設けて応
力の発生を抑えるようにしても良い。 Note that since the swinging member 19 swings at an eccentric position with respect to the axis of the fluid torque converter, the swinging changes the radial position of the connecting portion 22 with respect to the clutch plate 9 and the turbine wheel 7, and the turbine As the amount of displacement of the impeller 7 increases, the radial position of the connecting portion 22 shifts inward and the degree of curvature of the piano wire 24 increases, causing stress fatigue and the diameter acting through the piano wire 24. Due to stress in the outward direction, the connecting portion 22 and the pivot 2
Since there is a concern about uneven wear, etc., a joint point 24a may be provided in the middle of the piano wire 24, as shown in FIG. 4, to suppress the generation of stress.
又、上記実施例でピアノ線２４はスプリングワ
ツシヤ１０ａに固定したが、これに限るものでは
無く、例えば出力側リテーナ１６に固定しても良
く、更にはピアノ線２４を用いずに連結部２２に
おいて揺動部材１９とタービン翼車７とを一方の
ピンと他方の径方向の長孔とで係合連結するよう
にしても良い。 Further, in the above embodiment, the piano wire 24 is fixed to the spring washer 10a, but the invention is not limited to this. For example, the piano wire 24 may be fixed to the output side retainer 16, or the piano wire 24 may be fixed to the connecting portion 22 without using the piano wire 24. In this case, the swinging member 19 and the turbine wheel 7 may be engaged and connected by a pin on one side and a long hole in the radial direction on the other side.
この様に本考案によるときは、開閉弁を構成す
る揺動部材に備える弁部と、タービン翼車との連
結部との枢軸からの距離を適宜に設定することに
より、駆動トルクの所望の領域で連通孔の開度を
増減制御出来、クラツチ板の係合力の駆動トルク
に応じたより細かな制御を行うことが可能となる
効果を有する。 As described above, according to the present invention, the desired range of driving torque can be achieved by appropriately setting the distance from the pivot between the valve part provided in the swinging member constituting the on-off valve and the connection part with the turbine blade wheel. The opening degree of the communicating hole can be controlled to increase or decrease, which has the effect of making it possible to perform more detailed control of the engagement force of the clutch plate in accordance with the driving torque.
第１図は本案装置の１例の截断側面図、第２図
は第１図の−線で截断したクラツチ板の背面
部、第３図は第２図の−線截断側面図、第４
図は他の実施例のクラツチ板の背面図である。
１……流体トルクコンバータ本体、２……入力
軸、３……出力軸、４……入力ケース、５……ポ
ンプ翼車、６……内部空隙、７……タービン翼
車、９……クラツチ板、１０……ダンパスプリン
グ、１７……連通孔、１８……開閉弁、１９……
揺動部材、２０……枢軸、２１……弁部、２２…
…連結部。
Fig. 1 is a cross-sectional side view of an example of the device of the present invention, Fig. 2 is a rear side view of the clutch plate taken along the - line in Fig. 1, Fig. 3 is a side view taken along the - line in Fig. 2, and Fig. 4 is a cross-sectional side view of an example of the present device.
The figure is a rear view of a clutch plate of another embodiment. DESCRIPTION OF SYMBOLS 1... Fluid torque converter main body, 2... Input shaft, 3... Output shaft, 4... Input case, 5... Pump impeller, 6... Internal gap, 7... Turbine impeller, 9... Clutch Plate, 10... Damper spring, 17... Communication hole, 18... Open/close valve, 19...
Swinging member, 20... Pivot, 21... Valve portion, 22...
...Connection part.
Claims (1)
ケースに連結される他側のポンプ翼車とで囲われ
る流体トルクコンバータ本体の内部空隙に、出力
軸に連結されるタービン翼車と、該タービン翼車
と該入力ケースとの間のクラツチ板とを設け、該
クラツチ板を軸方向に移動自在としてその両側面
に作用させる流体圧力差に応じて該入力ケースに
係脱自在とすると共に、該クラツチ板と該タービ
ン翼車とをダンパスプリングを介して相対回転可
能に連結し、該クラツチ板に、その両側面間を連
通する連通孔と、該連通孔を開閉する開閉弁とを
設けて、該開閉弁を該タービン翼車の該クラツチ
板に対する逆転方向への相対回転で閉じ側に動作
させるようにしたものにおいて、該開閉弁を該ク
ラツチ板に枢着される揺動部材で構成し、該揺動
部材にその枢軸からの距離を適宜に設定して該連
通孔を開閉する弁部と、該タービン翼車の該相対
回転で該揺動部材を揺動させる該タービン翼車と
の連結部とを備えたことを特徴とする流体トルク
コンバータ用クラツチの作動制御装置。 A turbine impeller connected to the output shaft and a pump impeller connected to the output shaft are placed in an internal gap of the fluid torque converter main body surrounded by an input case on one side connected to the input shaft and a pump impeller on the other side connected to the input case. A clutch plate is provided between the turbine impeller and the input case, and the clutch plate is movable in the axial direction and can be freely engaged and disengaged from the input case in response to a fluid pressure difference acting on both sides of the clutch plate, The clutch plate and the turbine wheel are relatively rotatably connected via a damper spring, and the clutch plate is provided with a communication hole that communicates between both sides of the clutch plate, and an on-off valve that opens and closes the communication hole. , in which the on-off valve is operated to the closing side by relative rotation of the turbine wheel in a reverse direction with respect to the clutch plate, the on-off valve comprising a swinging member pivotally mounted on the clutch plate. , a valve part that opens and closes the communication hole by appropriately setting a distance from the pivot axis of the swinging member, and a turbine wheel that swings the swinging member with the relative rotation of the turbine wheel. 1. An operation control device for a clutch for a fluid torque converter, comprising: a connecting portion.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17561282U JPS5979660U (en) | 1982-11-22 | 1982-11-22 | Clutch operation control device for fluid torque converter |
| US06/505,753 US4638897A (en) | 1982-06-24 | 1983-06-20 | Damper device for a torque converter clutch |
| GB08317204A GB2123906B (en) | 1982-06-24 | 1983-06-24 | Torque converter with lock-up clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17561282U JPS5979660U (en) | 1982-11-22 | 1982-11-22 | Clutch operation control device for fluid torque converter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5979660U JPS5979660U (en) | 1984-05-29 |
| JPS6128129Y2 true JPS6128129Y2 (en) | 1986-08-21 |
Family
ID=30382017
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17561282U Granted JPS5979660U (en) | 1982-06-24 | 1982-11-22 | Clutch operation control device for fluid torque converter |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5979660U (en) |
-
1982
- 1982-11-22 JP JP17561282U patent/JPS5979660U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5979660U (en) | 1984-05-29 |
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