JPH03186620A - Hydraulic operation type clutch release bearing device - Google Patents
Hydraulic operation type clutch release bearing deviceInfo
- Publication number
- JPH03186620A JPH03186620A JP1322501A JP32250189A JPH03186620A JP H03186620 A JPH03186620 A JP H03186620A JP 1322501 A JP1322501 A JP 1322501A JP 32250189 A JP32250189 A JP 32250189A JP H03186620 A JPH03186620 A JP H03186620A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- clutch release
- release bearing
- stopper
- housing
- 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
- 230000002093 peripheral effect Effects 0.000 abstract description 7
- 239000010720 hydraulic oil Substances 0.000 abstract 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000000994 depressogenic effect Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/083—Actuators therefor
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明はマニュアルトランスミッション式自動車に使用
される油圧作動型クラッチレリーズ軸受装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulically actuated clutch release bearing device used in a manual transmission vehicle.
［従来の技術Ｊ
近年マニュアルトランスミッション式自動車のクラッチ
レリーズ軸受の駆動装置は、例えば実開昭５３−５９０
５４号、実開昭６０−１６７２３５号に開示されている
ように軽量化及びコストダウンの為、レリーズシリンダ
、レリーズフオ一り等を廃止し、その駆動部分をクラッ
チレリーズ軸受内に配備した油圧式クラッチ軸受に変更
されつつある。これらは、構成要素である軸受部、ハブ
部、シリンダ部が一直繰上に配置されている。即ち軸方
向に長い構造である。[Prior Art J] In recent years, drive devices for clutch release bearings in manual transmission vehicles have been developed, for example, in U.S. Pat.
As disclosed in No. 54 and Utility Model Application Publication No. 60-167235, in order to reduce weight and cost, the hydraulic clutch eliminates the release cylinder, release foo, etc., and places the driving part inside the clutch release bearing. It is being replaced by bearings. These components include a bearing section, a hub section, and a cylinder section that are arranged one above the other. That is, it has a long structure in the axial direction.
［発明が解決しようとする課題］
上述のように各構成要素が、−直線状に配置されている
のでの自動車の諸元上軸方向の寸法に制約がある場合に
十分なストローク量が確保できない、■それぞれの部品
を小型化、薄肉化するには、物理的に限界があり、アセ
ンブリとしての総幅寸法の最小値が決定される、■限界
に近い寸法で製作される場合、例えば軸受のポールサイ
ズが小さくなったり、シリンダブロックの肉厚が薄くな
ったりして耐久性、強度が不足する場合がある、■シリ
ンダブロックの厚みが薄くなった場合、作動油導入穴寸
法が小さくなり、穴加工の加工性が低下する、■ピスト
ン長さを十分にとれないため、ピストンとシリンダのガ
イド面が少なくなり、ピストンが抜けたり、ストローク
時における円滑な摺動連動を阻害する、などの種々の問
題があった。[Problem to be solved by the invention] As mentioned above, each component is arranged in a straight line, so if there are restrictions on the dimensions of the vehicle in the upper axial direction, a sufficient stroke amount cannot be secured. ■There are physical limits to making each part smaller and thinner, and the minimum total width of the assembly is determined. ■When manufacturing with dimensions close to the limit, for example, bearings If the pole size becomes smaller or the wall thickness of the cylinder block becomes thinner, durability and strength may be insufficient. There are various problems such as reduced machining efficiency, and insufficient piston length, which reduces the amount of guide surface between the piston and cylinder, causing the piston to come off or hinder smooth sliding interaction during stroke. There was a problem.
［課題を解決するための手段］
本発明は１回転軸に挿通される円筒部を設けた内側ハウ
ジングと、内側ハウジングの円筒部の外周側に嵌装され
両ハウジング間に油室を形成する外側ハウジングと、油
室に挿通され外端にクラッチレリーズ軸受を設けたピス
トンとから成る油圧作動型クラッチレリーズ軸受装置に
おいて、前記ピストンを外側ハウジグの開口端に当接す
るストッパを内端に有し、外端がクラッチレリーズ軸受
の端部に当接可能の外側ピストンと、外端にクラッチレ
リーズ軸受を設け、内端が外側ピストンの先端に設けた
ストッパに係合するストッパを内側に設けた内側ピスト
ンとの複ピストン構造とし、外周側ピストンが伸び切っ
た後、さらに内周側ピストンが伸びるようにして上述の
問題点を解決したものである。[Means for Solving the Problems] The present invention includes an inner housing provided with a cylindrical portion that is inserted through a rotating shaft, and an outer housing that is fitted on the outer peripheral side of the cylindrical portion of the inner housing and forms an oil chamber between the two housings. A hydraulically actuated clutch release bearing device consisting of a housing and a piston inserted into an oil chamber and provided with a clutch release bearing at its outer end, the piston having a stopper at its inner end that brings the piston into contact with an open end of an outer housing; an outer piston whose end can come into contact with the end of a clutch release bearing; an inner piston whose outer end is provided with a clutch release bearing; and whose inner end is provided with a stopper inside that engages with a stopper provided at the tip of the outer piston. The above-mentioned problem is solved by adopting a multi-piston structure, and after the outer piston is fully extended, the inner piston is further extended.
［作用］
次に、作動状態を説明する。まず第１図の状態から圧油
が油室（Ｉｌｌに導入されると、外側ピストン（７１１
、内側ピストン（７２）が同時に図面において左方向へ
比較的緩やかに動き出し、第２図に示すように外側ピス
トン（７１）の壁面（７１ｃｌが外側ハウジング（５）
の開口縁（５３）に当接し、外側ピストンの移動は停止
する。さらに圧油の供給が続くと内側ピストン（７２）
のみが速やかに動き、第３図に示すように内側ピストン
（７２）は、その壁面１７２ｄｌが外側ピストン（７１
）の小径側（７１ｆｌ と当接するまで移動する。この
時点で軸受の内輪＋１ｄｌの突出端ｆｌｄｌが図示しな
いダイヤフラムと軽く接触して回転している状態から、
ダイヤフラムを押圧し、クラッチの係合状態を脱して回
転を続ける。さらに、戻し方向（図面において右側）へ
作動させるには、油室（１１）の圧油を排出すると、図
示しないダイヤフラムスプリングのばね力により押し戻
される。[Operation] Next, the operating state will be explained. First, from the state shown in Figure 1, when pressure oil is introduced into the oil chamber (Ill), the outer piston (711
At the same time, the inner piston (72) begins to move relatively gently to the left in the drawing, and as shown in FIG.
The outer piston stops moving. When the supply of pressure oil continues, the inner piston (72)
As shown in FIG. 3, the wall surface 172dl of the inner piston (72)
) until it comes into contact with the small diameter side (71fl).At this point, the protruding end fldl of the inner ring +1dl of the bearing is in light contact with a diaphragm (not shown) and is rotating.
Press the diaphragm, disengage the clutch, and continue rotating. Furthermore, in order to operate in the return direction (to the right in the drawing), the pressure oil in the oil chamber (11) is discharged, and the spring force of a diaphragm spring (not shown) pushes it back.
［実施例］
次に、本発明の実施例を図面について説明する。なお、
実施例は内輪が図示しないダイヤフラムに接触していて
常に回転している常時接触型のものである。第１図は作
動前の状態を示し、図示しない回転軸に挿通される円筒
部（６１）と該円筒部の周端から、径方向外方に鍔状に
延びる延長部（６２）とからなる内側ハウジングｆ６１
と、内側ハウジングの延長部に嵌着された外側ハウジ
ング（５）との間に環状の油室（Ｉｌｌが形成される。[Example] Next, an example of the present invention will be described with reference to the drawings. In addition,
The embodiment is of a constant contact type in which the inner ring is in contact with a diaphragm (not shown) and constantly rotates. Fig. 1 shows the state before operation, and consists of a cylindrical part (61) inserted through a rotating shaft (not shown) and an extension part (62) extending radially outward from the peripheral end of the cylindrical part in the shape of a brim. inner housing f61
An annular oil chamber (Ill) is formed between the outer housing (5) and the outer housing (5) fitted into the extension of the inner housing.
該油室（Ｉｌｌには環状の外側ピストン（７１）と環状
の内側ピストン（７２）が装入され、これらピストンは
外側ハウジング（５）に穿設された圧油導入穴（５１）
を経て油室（１１）に流入した圧油の作用によって図面
において左方向に押圧される。An annular outer piston (71) and an annular inner piston (72) are inserted into the oil chamber (Ill), and these pistons are connected to a pressure oil introduction hole (51) bored in the outer housing (5).
It is pushed leftward in the drawing by the action of the pressure oil that has flowed into the oil chamber (11) through the.
外側ハウジング１５）の内径面（５２）に外側ピストン
（７１）の大・径の外周面が（７１ａｌが摺接すると共
に、外側ピストン（７１）の小径面（７１ｂ＋は、外側
ハウジング（５）の開口縁（５３）と摺動し、ストロ〜
り端において、壁面（７１ｃｌが外側ハウジングの開口
縁部（５３）と衝当して停止しストッパを形成する。The large diameter outer circumferential surface (71al) of the outer piston (71) is in sliding contact with the inner diameter surface (52) of the outer housing 15), and the small diameter surface (71b+ of the outer piston (71) is the opening of the outer housing (5). Slides on the edge (53) and strokes ~
At the end, the wall surface (71cl) abuts against the opening edge (53) of the outer housing to form a stop.
また、先端（７１ｄｌは後述する軸受に取付けられたハ
ブ（４）に当接し第２図に示す位置にクラッチレリーズ
軸受を移動させる。内側ピストン（７２）はその大径外
径面（７２ａｌが外側ピストン（７１）の内径面（７１
ｅ）と摺設すると共に、その内径面ｆ７２ｂｌが円筒部
（６１）の外径面（６１ａ）と摺接し、小径面（７２ｃ
ｌは外側ピストンの小径面（７１ｆｌ と摺接し、スト
ロークエンドにおいて、内側ピストンの壁面＋７２ｄｌ
と外側ピストン（７１）の小径側（７１ｆｌが衝当して
停止し、ストッパを形成する。Also, the tip (71dl) comes into contact with a hub (4) attached to a bearing, which will be described later, and moves the clutch release bearing to the position shown in Fig. 2.The inner piston (72) has its large diameter outer diameter surface (72al is the outer The inner diameter surface (71) of the piston (71)
e), the inner diameter surface f72bl is in sliding contact with the outer diameter surface (61a) of the cylindrical portion (61), and the small diameter surface (72c
l is in sliding contact with the small diameter surface (71fl) of the outer piston, and at the stroke end, the wall surface of the inner piston + 72dl
The small diameter side (71fl) of the outer piston (71) hits and stops, forming a stopper.
クラッチレリーズ軸受ｆｉｌ は転動体としてボールｆ
ｌａｔが内輪ｆｌｂｌ 、外輪（ｌｃ１間の介装され、
内輪１１ｂｌは外輪（ＩＣ）より６幅広に形成されると
共に、断面が円弧をなす突出端１１ｄｌが作動時に図示
しないダイヤフラムスプリングを押圧してクラッチを外
すようになっている。その際、内輪（１ｂ）は回転トル
クを受けて回転する。また、外輪の外径面側にはカバー
（３）がすきま（Ｓｌ を介して被嵌され、外輪の外端
面に位置する波ばね（２）の押圧力により外輪の内端が
ハブ（４） に押圧され軸受がフローティング支持され
る。これによりダイヤフラムスプリングの回転中心に軸
受が移動することができる。さらに、ハブ（４）の内周
端は内側ピストン（７２）の外端に取付けられ内側ピス
トンの移動に伴ってクラッチレリーズ軸受ｆｉｌ をさ
らに第３図に示す位置に移動させる。なお、（９ａ）は
外側ピストン（７１）の大径外周面に取付けられたシル
であり、（９ｂ）は内側ピストン（７２）の大径外径面
（７２ａｌに取付けられたシール、ｆｌｏｌは同内径面
に取付けられたシールである。The clutch release bearing fil uses balls f as rolling elements.
lat is interposed between the inner ring flbl and the outer ring (lc1,
The inner ring 11bl is formed to be 6 wider than the outer ring (IC), and a protruding end 11dl having an arcuate cross section presses a diaphragm spring (not shown) during operation to release the clutch. At this time, the inner ring (1b) receives rotational torque and rotates. In addition, a cover (3) is fitted on the outer diameter side of the outer ring through a gap (Sl), and the inner end of the outer ring is pressed against the hub (4) by the pressing force of the wave spring (2) located on the outer end face of the outer ring. The bearing is supported in a floating manner by being pressed by the diaphragm spring.This allows the bearing to move to the center of rotation of the diaphragm spring.Furthermore, the inner peripheral end of the hub (4) is attached to the outer end of the inner piston (72), and the inner peripheral end of the hub (4) is attached to the outer end of the inner piston (72). As the clutch release bearing fil moves, the clutch release bearing fil is further moved to the position shown in Fig. 3. Note that (9a) is a sill attached to the large diameter outer peripheral surface of the outer piston (71), and (9b) is a sill attached to the large diameter outer peripheral surface of the outer piston (71). A seal attached to the large-diameter outer diameter surface (72al) of the piston (72) and flol are seals attached to the inner diameter surface of the piston (72).
なお、実施例においてクラッチレリーズ軸受として、内
輪回転形のものが示されているが、これに代えて外輪回
転形のものを用いることができることはもちろんである
。In the embodiments, an inner ring rotating type clutch release bearing is shown, but it goes without saying that an outer ring rotating type can be used instead.
次に、作動状態を説明する。まず第１図の状態から圧油
が油室（１１）に導入されると、外側ピストン（７１）
、内側ピストン（７２）が同時に図面において左方向へ
比較的縁やかに動き出し、第２図に示すように外側ピス
トン（７１）の壁面（７１ｃｌが外側ハウジング（５）
の開口縁（５３）に当接し、外側ピストンの移動は停止
する。さらに圧油の供給が続くと内側ピストン（７２）
のみが速やかに動き、第３図に示すように内側ピストン
（７２）はその壁面（７２ａｌが外側ピストン（７１）
の小径側（７１ｆｌ と当接するまで移動する。この時
点で軸受の内輪ｆｌｄｌの突出端ｆｌｄｌが、図示しな
いダイヤフラムと軽く接触して回転している状態から、
ダイヤフラムスプリングをさらに押圧し、クラッチの係
合状態を脱して回転を続ける。さらに、戻し方向（図面
において右側）へ作動させるには、油室（１１）圧油を
排出すると、図示しないダイヤフラムスプリングのばね
力により押し戻されることになる。Next, the operating state will be explained. First, when pressure oil is introduced into the oil chamber (11) from the state shown in Figure 1, the outer piston (71)
At the same time, the inner piston (72) begins to move relatively smoothly to the left in the drawing, and as shown in FIG.
The outer piston stops moving. When the supply of pressure oil continues, the inner piston (72)
As shown in FIG. 3, the inner piston (72) moves quickly, and as shown in FIG.
At this point, the protruding end fldl of the inner ring fldl of the bearing is in light contact with a diaphragm (not shown) and is rotating.
The diaphragm spring is further pressed, the clutch is disengaged, and rotation continues. Furthermore, in order to operate in the return direction (to the right in the drawing), when the pressure oil in the oil chamber (11) is discharged, it is pushed back by the spring force of a diaphragm spring (not shown).
なお、本発明は実施例に示す常時接触型のものに代えて
クラッチペダルを踏み始めた瞬間にダイヤフラムスプリ
ングと内輪又は外輪が回転する所謂非接触型に適用でき
ることはもちろんである。It goes without saying that the present invention can be applied to a so-called non-contact type in which the diaphragm spring and the inner or outer ring rotate at the moment the clutch pedal is started to be depressed, instead of the constant contact type shown in the embodiment.
［効果］
本発明は上述のようにピストンを外側、内側の２重構造
としたため、外側ピストンが伸びきった後、さらに内側
ピストンが伸び、ピストン１個の場合に比べて長ストロ
ークを可能にする。又同ストロークの場合にはアッセン
ブリとして軸方向寸法を短かくすることができるのであ
り、軸方向の寸法の制約に伴う従来品の問題点はすべて
解決された。[Effects] As described above, the present invention has a piston with a double structure of outer and inner pistons, so after the outer piston is fully extended, the inner piston extends further, enabling a longer stroke than in the case of one piston. . Furthermore, in the case of the same stroke, the axial dimension of the assembly can be shortened, and all the problems of conventional products due to restrictions on the axial dimension have been solved.
本発明は複数のピストン構造であるため、作動途中でシ
リンダ断面積が小さくなり、一定の油量を送りつづける
と、最初はストロークスピードが近く、途中から速くな
るのであり、クラッチの踏み初め、いわゆる半クラッチ
の状態の時は、ゆっくりストロークし、踏み終り（クラ
ッチを切り離す時）にはす速くストロークするといった
、理想的なりラッチワークを提供することができる。Since the present invention has a multiple piston structure, the cross-sectional area of the cylinder decreases during operation, and if a constant amount of oil is continued to be sent, the stroke speed is close at first, but increases in the middle, and the stroke speed becomes faster when the clutch is first depressed. It is possible to provide ideal latch work in which the clutch strokes slowly when the clutch is in a half-clutch state, and quickly strokes at the end of the clutch (when releasing the clutch).
図面は本発明の実施例の断面図であり、第１図は作動前
の状態、第２図は作動途中、第３図はストロークエンド
の各状態図である。
１・・・クラッチレリーズ軸受け、１１・・・油室、４
・・・端部、５−・−外側ハウジング、５３−・・開口
縁、（ストッパ）、６・−・内側ハウジング、６１・・
・円筒部、７１・・−外側ピストン、７１ｃ・−・壁面
（ストッパ）、了１ｆ・・・小径面〔ストッパ）、７２
．・内側ピストン、７２ｄ・・・壁面（ストッパ）。The drawings are sectional views of an embodiment of the present invention, with FIG. 1 showing the state before operation, FIG. 2 showing the state during operation, and FIG. 3 showing each state at the end of the stroke. 1...Clutch release bearing, 11...Oil chamber, 4
...End, 5--Outer housing, 53--Opening edge, (stopper), 6--Inner housing, 61--
・Cylindrical part, 71...-Outer piston, 71c...Wall surface (stopper), 1f...Small diameter surface [stopper], 72
．． -Inner piston, 72d...wall surface (stopper).
Claims (1)
ング（６）と、内側ハウジングの円筒部の外周側に嵌装
され両ハウジング間に油室（１１）を形成する外側ハウ
ジング（５）と、油室に挿通され外端にクラッチレリー
ズ軸受（１）を設けたピストンとから成る油圧作動型ク
ラッチレリーズ軸受装置において、前記ピストンを外側
ハウジング（５）の開口縁（５３）に当接するストッパ
（７１ｃ）を内端に有し、外端がクラッチレリーズ軸受
（１）の端部（４）に当接可能の外側ピストン（７１）
と、外端にクラッチレリーズ軸受（１）を設け、内端が
外側ピストンの先端に設けたストッパ（７１ｆ）に係合
するストッパ（７２ｄ）を内側に設けた内側ピストンと
の複ピストン構造としたことを特徴とする油圧作動型ク
ラッチレリーズ軸受装置。An inner housing (6) provided with a cylindrical portion (61) that is inserted through the rotating shaft, and an outer housing (5) that is fitted onto the outer circumferential side of the cylindrical portion of the inner housing and forms an oil chamber (11) between the two housings. and a piston that is inserted into an oil chamber and has a clutch release bearing (1) at its outer end, a stopper that brings the piston into contact with an opening edge (53) of an outer housing (5) (71c) at the inner end and whose outer end can come into contact with the end (4) of the clutch release bearing (1)
The clutch release bearing (1) is provided at the outer end, and the inner piston has a multi-piston structure in which the inner end is provided with a stopper (72d) that engages with the stopper (71f) provided at the tip of the outer piston. A hydraulically actuated clutch release bearing device characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1322501A JP2775326B2 (en) | 1989-12-14 | 1989-12-14 | Hydraulically operated clutch release bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1322501A JP2775326B2 (en) | 1989-12-14 | 1989-12-14 | Hydraulically operated clutch release bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03186620A true JPH03186620A (en) | 1991-08-14 |
| JP2775326B2 JP2775326B2 (en) | 1998-07-16 |
Family
ID=18144355
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1322501A Expired - Lifetime JP2775326B2 (en) | 1989-12-14 | 1989-12-14 | Hydraulically operated clutch release bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2775326B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1995009312A1 (en) * | 1993-09-29 | 1995-04-06 | Valeo | Pull-type hydraulic motor vehicle clutch |
| WO1997001716A1 (en) * | 1995-06-24 | 1997-01-16 | INA Wälzlager Schaeffler oHG | Hydraulic disengaging device for a friction clutch |
| DE19636399A1 (en) * | 1995-09-19 | 1997-03-20 | Valeo | Pressure-operated ram for automotive diaphragm clutch |
| FR2738884A1 (en) * | 1995-09-19 | 1997-03-21 | Valeo | CYLINDER WITH TWO CONTROL CHAMBERS AND RELEASE STOPPER PROVIDED WITH SUCH A CYLINDER |
| WO1997042426A1 (en) * | 1996-05-03 | 1997-11-13 | Automotive Products France S.A. | Hydraulic actuators |
| DE4407665B4 (en) * | 1994-03-09 | 2005-09-22 | Zf Sachs Ag | Hydraulically actuated release system |
| JP2005291498A (en) * | 2004-03-31 | 2005-10-20 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | Hydraulic release system |
| JP2011226492A (en) * | 2010-04-15 | 2011-11-10 | Exedy Corp | Hydraulic clutch release cylinder device and clutch release device including the same |
-
1989
- 1989-12-14 JP JP1322501A patent/JP2775326B2/en not_active Expired - Lifetime
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2712948A1 (en) * | 1993-09-29 | 1995-06-02 | Valeo | Motor vehicle clutch device of the pulled type and hydraulically actuated. |
| WO1995009312A1 (en) * | 1993-09-29 | 1995-04-06 | Valeo | Pull-type hydraulic motor vehicle clutch |
| US5655639A (en) * | 1993-09-29 | 1997-08-12 | Valeo | Motor vehicle hydraulic clutch assembly of the pull to release type |
| DE4407665B4 (en) * | 1994-03-09 | 2005-09-22 | Zf Sachs Ag | Hydraulically actuated release system |
| KR100419704B1 (en) * | 1995-06-24 | 2004-10-22 | 루크 라멜렌 운트 쿠프룽스바우 베타일리궁스 카게 | Hydraulic separator for friction clutches |
| WO1997001716A1 (en) * | 1995-06-24 | 1997-01-16 | INA Wälzlager Schaeffler oHG | Hydraulic disengaging device for a friction clutch |
| DE19680489B4 (en) * | 1995-06-24 | 2006-05-24 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic release device for a friction clutch |
| DE19636399A1 (en) * | 1995-09-19 | 1997-03-20 | Valeo | Pressure-operated ram for automotive diaphragm clutch |
| US5732811A (en) * | 1995-09-19 | 1998-03-31 | Valeo | Ram with two control chambers and a clutch release bearing provided with such a ram |
| DE19636399B4 (en) * | 1995-09-19 | 2006-03-30 | Valeo | Pressure cylinder with a displaceable intermediate chamber |
| FR2738884A1 (en) * | 1995-09-19 | 1997-03-21 | Valeo | CYLINDER WITH TWO CONTROL CHAMBERS AND RELEASE STOPPER PROVIDED WITH SUCH A CYLINDER |
| WO1997042426A1 (en) * | 1996-05-03 | 1997-11-13 | Automotive Products France S.A. | Hydraulic actuators |
| JP2005291498A (en) * | 2004-03-31 | 2005-10-20 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | Hydraulic release system |
| JP2011226492A (en) * | 2010-04-15 | 2011-11-10 | Exedy Corp | Hydraulic clutch release cylinder device and clutch release device including the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2775326B2 (en) | 1998-07-16 |
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