WO1991019113A1 - Clutch device - Google Patents

Clutch device Download PDF

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Publication number
WO1991019113A1
WO1991019113A1 PCT/JP1991/000617 JP9100617W WO9119113A1 WO 1991019113 A1 WO1991019113 A1 WO 1991019113A1 JP 9100617 W JP9100617 W JP 9100617W WO 9119113 A1 WO9119113 A1 WO 9119113A1
Authority
WO
WIPO (PCT)
Prior art keywords
release
clutch
pressure plate
projection
bearing
Prior art date
Application number
PCT/JP1991/000617
Other languages
French (fr)
Japanese (ja)
Inventor
Kouji Kajitani
Minoru Abe
Tetuji Takano
Original Assignee
Kabushiki Kaisha Daikin Seisakusho
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 Kabushiki Kaisha Daikin Seisakusho filed Critical Kabushiki Kaisha Daikin Seisakusho
Publication of WO1991019113A1 publication Critical patent/WO1991019113A1/en

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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
    • 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
    • F16D25/085—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 the clutch actuation being of the pull type

Definitions

  • the present invention relates to a clutch device in which a clutch disk facing is arranged between a flywheel and a pre-sharp rate, and the clutch is intermittently intermittently moved by an axial movement of the pressure rate plate.
  • FIG. 2 shows a conventional example of a pull-type clutch.
  • the outer fulcrum is supported by the clutch cover 2 and the intermediate fulcrum is the pre-sharp plate 6.
  • contact, c i.e. the diaphragm spring 3 1 inner peripheral support portion is engaged with the Lelie Zusuri over Bed 3 3 and serves to impart imposition load plexes sharp rate 6, Lelie Zusu Li when release - Bed It serves as a transmission lever for transmitting the release from 3 to pressure plate 6.
  • the structure of the diaphragm spring 31 itself becomes a complicated shape having a so-called many radial slits and the like. Trouble occurs, transmission efficiency of release force is not good, and release operation performance is unstable.
  • An object of the present invention is to eliminate the loss of the release stroke and improve the release operation performance.
  • the present invention provides a clutch in which a clutch disk facing is arranged between a flywheel and a press plate, and the clutch is interrupted by moving the press plate in the axial direction.
  • a projection part extending toward the axis is integrally formed on the plate shear plate, and a release bearing for directly engaging a release bearing with the projection and supporting the release bearing is provided.
  • the valve can be moved in the axial direction by a hydraulic cylinder.
  • FIG. 1 is a longitudinal sectional view of a clutch device to which the present invention is applied
  • FIG. 2 is a longitudinal sectional view of a conventional example.
  • FIG. 1 showing a longitudinal sectional view of a clutch device to which the present invention is applied
  • a flywheel 1 of the clutch is connected to an engine output shaft via a flywheel damper F.
  • the facing 9 of the clutch disk 5 and the pre-sharp rate 6 are arranged in order from the flywheel side.
  • the clutch disk 5 has an inner spline hub 5a spline-fitted to an output shaft (not shown).
  • the pre-sharp plate 6 has its outer peripheral projection 6 c clamped through a plurality of strap plates 12. It is connected to the tab cover 2 so as to be movable in the axial direction.
  • the rear end face of the pressure plate 6 is formed with a full clamp 6b projecting rearward.
  • An axis is provided between the full clamp 6b and the projection 2a of the rear end wall of the clutch cover 2.
  • a disc spring 15 is contracted by itself in the directional compression, and the disc spring 15 urges the pre-sharper plate 6 forward to press against the facing 9.
  • the inner peripheral end of the disc spring 15 is fixed to the funnel clamland 6b by the clip 10 and the clip 10 is fixed to the pressure plate 6 by the rebate 11 .
  • annular projection 6a protruding toward the axis is integrally formed on the inner peripheral surface of the rear part of the pressure plate 6, an annular projection 6a protruding toward the axis is integrally formed.
  • an outer race of a relief bearing 20 arranged on the axis side is provided on the other hand.
  • An outwardly extending annular flange portion 22a is integrally formed with the projection 22.
  • the rear surface of the annular flange portion 22a is in contact with the projection 6a.
  • the inner race 21 of the release bearing 20 is fixed to the release sleeve 24 so that it cannot move in the axial direction.
  • the rear part of the release sleeve 24 is axially movably fitted to the hydraulic cylinder 23 via seals 25 and 26, and the oil chamber 27 in the hydraulic cylinder 23 is an oil port. It communicates with a hydraulic control mechanism (not shown) via 30. By supplying hydraulic oil into the oil chamber 27, the release sleeve 24 is moved rearward.
  • a conical stopper / damper spring 28 is disposed in the oil chamber 27 so as to be axially compressible.
  • FIG. 1 shows the clutch connection state, in which the oil chamber 27 of the hydraulic cylinder 23 is in an open state, and the pressure plate 6 is applied to the facing 9 by the elastic force of the disc spring 15. We are in pressure contact.
  • the projection 6a on the inner peripheral side of the pre-sharp plate 6 is an annular projection, but it may be a projection having a structure in which a slit for cooling air is formed radially.
  • the present invention is not limited to a structure in which the flywheel 1 is directly connected to the engine output shaft via a flywheel damper F as shown in FIG. It can also be applied to clutches that have a damper on the clutch disk.
  • a sleeve that directly engages the projection 6 a formed on the pressure plate 6 with the release bearing 20 and supports the ⁇ 0 release bearing 20. Since the hydraulic cylinder 23 allows the axis 24 to move in the axial direction, the hydraulic cylinder 23 does not require a lever component such as a diaphragm spring. Direct transmission is possible, so there is no loss of the release opening, and the transmission efficiency of the release force is improved and the release operation performance is improved.
  • a spring having a simple structure that can be simply contracted between the clutch cover 12 and the pressure plate 6 can be used.

Landscapes

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

Abstract

An object of the present invention is to eliminate the loss in the release stroke, thus improving the release operation performance. The present invention provides a clutch device wherein a facing (9) of a clutch disc (5) is interposed between a fly wheel (1) and a pressure plate (6), an axial movement of the pressure plate (6) connects or disconnects a clutch, a projecting portion (6a) extending toward the axis is integrally formed on the pressure plate (6) to directly engage a release bearing (20) with the projecting portion (6a), and a release sleeve (24) for supporting the release bearing (20) is made movable in the axial direction by a hydraulic cylinder (23).

Description

明細書  Specification
クラ ッチ装置  Clutch device
技術分野  Technical field
本発明は、 フライホイールとプレッ シャープレー トの間に クラ ッチディ スクのフエ一 シングを配置し、 プレッ シャ ープ レー 卜の軸方向の移動により クラ ッチを断続するクラ ッチ装 置に関する。  The present invention relates to a clutch device in which a clutch disk facing is arranged between a flywheel and a pre-sharp rate, and the clutch is intermittently intermittently moved by an axial movement of the pressure rate plate.
背景技術  Background art
第 2図はプルタイプ形クラ ッチの従来例を示しており、 ダ ィャフラムばね 3 1は、 その外周支点部がクラ ッチカバー 2 に支持されると共に中間支点部がプレッ シャープレ— ト 6に 当接し、 内周支点部がレリ ーズスリ ーブ 3 3に係合している c 即ちダイヤフラムばね 3 1 はプレッ シャープレー ト 6に押し 付け荷重を付与する役目と、 レリーズする際にレリ ーズス リ —ブ 3 3からプレッ シャ ープレ— ト 6にレリ —ズカを伝達す る伝達レバ—の役目を果している。 FIG. 2 shows a conventional example of a pull-type clutch. In the diaphragm spring 31, the outer fulcrum is supported by the clutch cover 2 and the intermediate fulcrum is the pre-sharp plate 6. contact, c i.e. the diaphragm spring 3 1 inner peripheral support portion is engaged with the Lelie Zusuri over Bed 3 3 and serves to impart imposition load plexes sharp rate 6, Lelie Zusu Li when release - Bed It serves as a transmission lever for transmitting the release from 3 to pressure plate 6.
ところがこのようにダイヤフラムばねを利用すると、 ダイ ャフラムばね 3 1 自体の構造がいわゆる多数の放射状のスリ ッ ト等を有する複雑な形状となり、 しかもレリ ーズ動作時に はダイヤフラムばね 3 1のたわみによるス ト ローク ロスが生 じ、 レリ ーズ力の伝達効率がよく なく、 レリ ーズ操作性能が 不安定である。  However, when the diaphragm spring is used as described above, the structure of the diaphragm spring 31 itself becomes a complicated shape having a so-called many radial slits and the like. Trouble occurs, transmission efficiency of release force is not good, and release operation performance is unstable.
(発明の目的）  (Object of the invention)
本発明の目的は、 レリ ーズス トロークのロスをなく し、 レ リ ーズ操作性能の向上を図ることである。  An object of the present invention is to eliminate the loss of the release stroke and improve the release operation performance.
発明の開示 (技術的手段） Disclosure of the invention (Technical means)
上記目的を達成するために本発明は、 フライホイ ールとプ レッ シャープレー 卜の間にクラ ッチディ スクのフエ一シング を配置し、 プレッ シャープレー 卜の軸方向の移動により クラ ツチを断続するクラッチ装置において、 プレツ シャ—プレー トに軸芯側に延びる突起部を一体に形成して、 該突起部にレ リ 一ズ軸受を直接係合し、 レリ ーズ軸受を支持するレリ ーズ スリ ーブを、 液圧シリ ンダにより軸方向に移動可能としてい る。  In order to achieve the above object, the present invention provides a clutch in which a clutch disk facing is arranged between a flywheel and a press plate, and the clutch is interrupted by moving the press plate in the axial direction. In the apparatus, a projection part extending toward the axis is integrally formed on the plate shear plate, and a release bearing for directly engaging a release bearing with the projection and supporting the release bearing is provided. The valve can be moved in the axial direction by a hydraulic cylinder.
(作用）  (Action)
レリ —ズする時には、 液圧シリ ンダを作動させることによ り レリ 一ズ軸受を軸方向に移動させ、 レリ 一ズ軸受によりプ レツ シャ一プレー トを直接引っ張り、 レリ ーズする。  When releasing, the hydraulic bearing is moved to move the bearing in the axial direction, and the release bearing directly pulls the release plate to release.
図面の簡単な説明  BRIEF DESCRIPTION OF THE FIGURES
第 1図は本発明を適用したクラッチ装置の縱断面図、 第 2 図は従来例の縱断面図である。  FIG. 1 is a longitudinal sectional view of a clutch device to which the present invention is applied, and FIG. 2 is a longitudinal sectional view of a conventional example.
発明を実施するための最良の態様  BEST MODE FOR CARRYING OUT THE INVENTION
本発明を適用したクラ ッチ装置の縱断面図を示す第 1図に おいて、 クラ ッチのフライホイ ール 1 はフライホイ ールダン パー Fを介してエンジン出力軸に連結されている。 フライホ ィ―ル 1の後端面に固着されたクラッチカバ— 2内には、 フ ライホイール側から順にクラッチディ スク 5のフエ一シング 9及びプレッ シャープレー ト 6が配置されている。 クラッチ ディ スク 5は内周スプライ ンハブ 5 aが図示しない出力軸に スプライ ン嵌合している。 プレッ シャープレー ト 6はその外 周突起部 6 cが複数のス トラッププレー ト 1 2を介してクラ ツチカバー 2に軸方向移動可能に連結されている。 In FIG. 1 showing a longitudinal sectional view of a clutch device to which the present invention is applied, a flywheel 1 of the clutch is connected to an engine output shaft via a flywheel damper F. In the clutch cover 2 fixed to the rear end face of the flywheel 1, the facing 9 of the clutch disk 5 and the pre-sharp rate 6 are arranged in order from the flywheel side. The clutch disk 5 has an inner spline hub 5a spline-fitted to an output shaft (not shown). The pre-sharp plate 6 has its outer peripheral projection 6 c clamped through a plurality of strap plates 12. It is connected to the tab cover 2 so as to be movable in the axial direction.
プレッ シャ ープレー ト 6の後端面には後方に突出するフル クラムラ ン ド 6 bが形成され、 該フルクラムラ ン ド 6 b とク ラ ッチカバ— 2の後端壁の突起 2 aの間には、 軸方向圧縮自 在に皿ばね 1 5が縮設されており、 該皿ばね 1 5によりプレ ッ シャープレ— ト 6を前方に付勢してフエ一シング 9に圧接 している。 皿ばね 1 5の内周端部はク リ ップ 1 0によりフノレ クラムラン ド 6 bに固定されており、 ク リ ップ 1 0はリベヅ ト 1 1でプレッ シャ ープレー ト 6に固定されている。  The rear end face of the pressure plate 6 is formed with a full clamp 6b projecting rearward. An axis is provided between the full clamp 6b and the projection 2a of the rear end wall of the clutch cover 2. A disc spring 15 is contracted by itself in the directional compression, and the disc spring 15 urges the pre-sharper plate 6 forward to press against the facing 9. The inner peripheral end of the disc spring 15 is fixed to the funnel clamland 6b by the clip 10 and the clip 10 is fixed to the pressure plate 6 by the rebate 11 .
プレッ シャ ープレー ト 6の後部の内周面には軸芯側に突出 する環状の突起部 6 aが一体に形成されており、 一方軸芯側 に配置されたレリ —ズ軸受 2 0のアウター レース 2 2には外 向きの環状つば部 2 2 aが一体に形成されており、 該環状つ ば部 2 2 aの後面が前記突起部 6 aに当接している。 レリ ー 軸受 2 0のイ ンナー レース 2 1 はレリ ーズス リ ーブ 2 4に軸 方向移動不能に固定されている。  On the inner peripheral surface of the rear part of the pressure plate 6, an annular projection 6a protruding toward the axis is integrally formed. On the other hand, an outer race of a relief bearing 20 arranged on the axis side is provided. An outwardly extending annular flange portion 22a is integrally formed with the projection 22. The rear surface of the annular flange portion 22a is in contact with the projection 6a. The inner race 21 of the release bearing 20 is fixed to the release sleeve 24 so that it cannot move in the axial direction.
レリ ーズスリ ーブ 2 4の後部はシール 2 5、 2 6を介して 油圧シリ ンダ 2 3に軸方向移動自在に嵌合しており、 油圧シ リ ンダ 2 3内の油室 2 7は油口 3 0を介して図示しない油圧 制御機構に連通している。 油室 2 7内に作動油を供給するこ とにより レリ ーズスリ ーブ 2 4を後方に移動させるようにな つている。 また油室 2 7には円錐状のス ト ッパ—兼ダンパ― ばね 2 8が軸方向圧縮自在に配置されている。  The rear part of the release sleeve 24 is axially movably fitted to the hydraulic cylinder 23 via seals 25 and 26, and the oil chamber 27 in the hydraulic cylinder 23 is an oil port. It communicates with a hydraulic control mechanism (not shown) via 30. By supplying hydraulic oil into the oil chamber 27, the release sleeve 24 is moved rearward. A conical stopper / damper spring 28 is disposed in the oil chamber 27 so as to be axially compressible.
作動を説明する。 第 1図はクラッチ接続状態を示しており、 油圧シリ ンダ 2 3の油室 2 7は開放状態であり、 プレツ シャ 一プレー ト 6は皿ばね 1 5の弾性力によりフエ一シング 9に 圧接している。 The operation will be described. FIG. 1 shows the clutch connection state, in which the oil chamber 27 of the hydraulic cylinder 23 is in an open state, and the pressure plate 6 is applied to the facing 9 by the elastic force of the disc spring 15. We are in pressure contact.
レリ —ズする場合には、 油圧制御機構により油圧シリ ンダ 2 3の油室 2 7に作動油を供給する。 そうするとレリ ーズ スリ ーブ 2 4と一体的にレ リ ーズ軸受 2 0が後方に移動し、 環状つば部 2 2 aにより直接プレッ シャ ープレー ト 6を皿ば ね 1 5に抗して後方に移動し、 プレッ シャ ープレー ト 6をフ エ ー シング 9から離す。  When releasing, hydraulic oil is supplied to the oil chamber 27 of the hydraulic cylinder 23 by the hydraulic control mechanism. Then, the release bearing 20 is moved rearward integrally with the release sleeve 24, and the pressure plate 6 is directly rearwardly opposed to the counter spring 15 by the annular collar 22a. To move the pressure plate 6 away from the facing 9.
発明を実施するための別の態様  Another embodiment for carrying out the invention
第 1図ではプレツ シャープレー ト 6の内周側の突起部 6 a を環状突起部としているが、 冷却風用のスリ ッ トを放射状に 形成した構造の突起とすることもできる。  In FIG. 1, the projection 6a on the inner peripheral side of the pre-sharp plate 6 is an annular projection, but it may be a projection having a structure in which a slit for cooling air is formed radially.
また本発明は、 第 1図のようにフライホイールダンバ— F を介してエンジン出力軸に連動連結される構造に限定される ものではなく、 フライホイール 1が直接エンジン出力軸に連 5 動連結され、 クラ ッチディ スクにダンパーを備えたようなク ラ ッチにも適用できる。  Further, the present invention is not limited to a structure in which the flywheel 1 is directly connected to the engine output shaft via a flywheel damper F as shown in FIG. It can also be applied to clutches that have a damper on the clutch disk.
発明の効果  The invention's effect
以上説明したように本発明は、 プレッ シャ ープレー ト 6に —体形成された突起部 6 aをレリ一ズ軸受 2 0に直接係合し- 0 レリ ーズ軸受 2 0を支持するレリ —ズスリ ーブ 2 4を、 液圧 シリ ンダ 2 3により軸方向移動可能としているので、 ダイヤ フラムばね等のレバ—部品を介さずに、 液圧シリ ンダ 2 3に より レリーズカをプレッ シャープレー ト 6に直接伝達できる, 従ってレリ ーズス ト口一クのロスが生じることはなく、 レリ 5 ーズ力の伝達効率が向上し、 レリーズ操作性能が向上する。  As described above, according to the present invention, there is provided a sleeve that directly engages the projection 6 a formed on the pressure plate 6 with the release bearing 20 and supports the −0 release bearing 20. Since the hydraulic cylinder 23 allows the axis 24 to move in the axial direction, the hydraulic cylinder 23 does not require a lever component such as a diaphragm spring. Direct transmission is possible, so there is no loss of the release opening, and the transmission efficiency of the release force is improved and the release operation performance is improved.
またプレッ シャ ープレー ト 6の押付け荷重を付与するため のばねと して、 クラ ッチカバ '一 2 とプレッ シャ ープレー 卜 6 の間に縮設されるだけの簡単な構造のものを使用できる。 Also, to apply the pressing load of pressure plate 6 As the spring, a spring having a simple structure that can be simply contracted between the clutch cover 12 and the pressure plate 6 can be used.
産業上の利用可能性  Industrial applicability
レ リ ーズス ト ロークのロスをなく し、 レ リ —ズ操作性能が 向上するので、 自動車用のクラ ッチ装置と して最適である。  Since the loss of the release stroke is eliminated and the release operation performance is improved, it is optimal as a clutch device for automobiles.

Claims

請求の範囲 The scope of the claims
1. フライホイール （ 1 ) とプレッ シャープレー ト （ 6 ) の間にクラ ッチディ スク （ 5 ) のフエ—シング （ 9 ) を配置 し、 プレッ シャープレー ト （6) の軸方向の移動により クラ ッチを断続するクラッチ装置において、 プレツ シャ—プレー ト （ 6) に軸芯側に延びる突起部 （ （6 a ) を一体に形成し て、 該突起部 （6 a ) にレリ —ズ軸受 （2 0 ) を直接係合し、 レリ一ズ軸受 （ 2 0 ) を支持するレリ ーズスリ ーブ （ 24 ) を、 液圧シリ ンダ （2 3) により軸方向に移動可能としてい ることを特徴とするクラ ッチ装置。  1. Place the clutch disc (5) facing (9) between the flywheel (1) and the pre-sharp rate (6), and move the pre-sharp rate (6) in the axial direction. In a clutch device that intermittently engages, a projection ((6a)) extending toward the shaft center is integrally formed on the plate shear plate (6), and a relief bearing (2) is formed on the projection (6a). 0) is directly engaged, and the release sleeve (24) supporting the release bearing (20) can be moved in the axial direction by the hydraulic cylinder (23). Clutch equipment.
5 Five
PCT/JP1991/000617 1990-05-30 1991-05-09 Clutch device WO1991019113A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2/142398 1990-05-30
JP2142398A JPH0833165B2 (en) 1990-05-30 1990-05-30 Clutch device

Publications (1)

Publication Number Publication Date
WO1991019113A1 true WO1991019113A1 (en) 1991-12-12

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ID=15314428

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Application Number Title Priority Date Filing Date
PCT/JP1991/000617 WO1991019113A1 (en) 1990-05-30 1991-05-09 Clutch device

Country Status (3)

Country Link
JP (1) JPH0833165B2 (en)
DE (1) DE4191212T (en)
WO (1) WO1991019113A1 (en)

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US5400887A (en) * 1992-08-07 1995-03-28 Kabushiki Kaisha Daikin Seisakusho Clutch cover assembly

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5400887A (en) * 1992-08-07 1995-03-28 Kabushiki Kaisha Daikin Seisakusho Clutch cover assembly
US5551547A (en) * 1992-08-07 1996-09-03 Kabushiki Kaisha Daikin Seisakusho Clutch cover assembly

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DE4191212T (en) 1992-05-14
JPH0434219A (en) 1992-02-05
JPH0833165B2 (en) 1996-03-29

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