JP2010084892A - Disc spring assembly - Google Patents

Disc spring assembly Download PDF

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Publication number
JP2010084892A
JP2010084892A JP2008256359A JP2008256359A JP2010084892A JP 2010084892 A JP2010084892 A JP 2010084892A JP 2008256359 A JP2008256359 A JP 2008256359A JP 2008256359 A JP2008256359 A JP 2008256359A JP 2010084892 A JP2010084892 A JP 2010084892A
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Prior art keywords
disc spring
outer peripheral
peripheral end
claw
annular
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Japanese (ja)
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Susumu Kobayashi
進 小林
Shigeo Takahashi
繁雄 高橋
Hideji Sadakari
秀治 貞苅
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Aisin Corp
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Aisin Seiki Co Ltd
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  • Springs (AREA)
  • Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a disc spring assembly, capable of exhibiting a centering force by a disc spring without a rise of cost. <P>SOLUTION: The disc spring assembly includes a predetermined member 6 having a mount part 6a extending in the axial direction, a claw part 6b formed on the top outer circumferential surface of the mount part 6a, and a stepped part 6c formed on the terminal outer circumferential surface of the mount part 6a; an annular member 5a disposed on the outer circumference of the mount part 6a and abutting on the stepped part 6c; and a disc spring 8 disposed on the outer circumference of the mount part 6a, and biases the annular member 5a toward the stepped part 6c with its inner circumferential end portion being caught by the claw part 6b and its outer circumferential end portion abutting on the annular member 5a. The inner circumferential end portion of the disc spring 8 pressure-contacts with the claw part 6b and the outer circumferential surface of the mount part 6a, and the outer circumferential end portion of the disc spring 8 pressure-contacts with the annular member 5a, whereby the disc spring 8 is incorporated with elastic deformation. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、所定の部材に環状部材を一体係合させる皿バネを組付けた皿バネ組付体に関する。   The present invention relates to a disc spring assembly in which a disc spring for integrally engaging an annular member with a predetermined member is assembled.

所定の部材に環状部材を一体係合させる皿バネを組付けた皿バネ組付体として、例えば、内側ハウジングと外側ハウジングの間にスライド可能に配された環状ピストンにレリーズベアリングを一体係合させる皿バネを組付けた油圧式クラッチレリーズ装置がある。油圧式クラッチレリーズ装置では、皿バネの内周端部が環状ピストンのクラッチ側の先端部近傍の外周面に形成された爪部に引っ掛かり、皿バネの外周端部がレリーズベアリング（例えば、外輪又は内輪）を環状ピストンに形成された段差部（フランジ部）に押さえ込むことで、環状ピストンにレリーズベアリングが調芯可能に一体係合している。   As a disc spring assembly in which a disc spring for integrally engaging an annular member with a predetermined member is assembled, for example, a release bearing is integrally engaged with an annular piston slidably disposed between an inner housing and an outer housing. There is a hydraulic clutch release device with a disc spring. In the hydraulic clutch release device, the inner peripheral end of the disc spring is caught by a claw formed on the outer peripheral surface near the tip of the annular piston on the clutch side, and the outer peripheral end of the disc spring is a release bearing (for example, an outer ring or The release bearing is integrally engaged with the annular piston so as to be aligned by pressing the inner ring into a stepped portion (flange) formed on the annular piston.

例えば、特許文献１では、転動する転動体を介在させる２つの同心的なレースを有する転がり軸受からなるクラッチ解離軸受であって、前記転がり軸受が、ポリマー材料から成るシフトスリーブ上に半径方向でシフト可能に配置されており、かつ前記転がり軸受の一方のレースが、前記シフトスリーブの半径方向外向きフランジと皿ばねとの間に締込まれた半径方向内向きフランジを有し、前記皿ばねがその半径方向内位範囲で、前記シフトスリーブの周溝内で夫々支持されている複数の舌片部に分割されている形式のものが開示されている。   For example, Patent Document 1 discloses a clutch disengagement bearing including a rolling bearing having two concentric races in which rolling elements that roll are interposed, and the rolling bearing is radially disposed on a shift sleeve made of a polymer material. The disc spring is arranged so as to be shiftable and one race of the rolling bearing has a radially inward flange clamped between a radially outward flange and a disc spring of the shift sleeve; Is disclosed that is divided into a plurality of tongue pieces that are respectively supported in the circumferential groove of the shift sleeve in the radially inner range.

特開昭６２−２８３２２１号公報Japanese Patent Laid-Open No. 62-283221 特開２００２−３４００２２号公報JP 2002-340022 A

皿バネを環状ピストンに組付ける際、皿バネの内周端部は、環状ピストンの爪部によって外周側に一旦広がってから内周側に狭まる過程で、皿バネの内周端部が外周側に広がったときに塑性変形を伴うので、皿バネがレリーズベアリングを環状ピストンの段差部（フランジ部）に押さえ付ける荷重が狙い通りに出せないことがある。また、皿バネの内周端部が外周側に広がったときの塑性変形によって皿バネの内周端部が環状ピストンの外周面に接触しない状態になることがあり、皿バネによる調芯力が減少することがある。   When the disc spring is assembled to the annular piston, the inner peripheral end of the disc spring is once expanded to the outer peripheral side by the claw portion of the annular piston and then narrowed to the inner peripheral side. Since the plate spring is accompanied by plastic deformation, the load by which the disc spring presses the release bearing against the step portion (flange portion) of the annular piston may not be produced as intended. In addition, the inner peripheral end of the disc spring may not be in contact with the outer peripheral surface of the annular piston due to plastic deformation when the inner peripheral end of the disc spring spreads to the outer peripheral side. May decrease.

ところで、特許文献２では、組付け時に皿バネを環状ピストンに圧入しないで、ピストン部材の反シリンダ空間側に皿ばねガイドを配置し、そこに収容される皿ばねを介してクラッチレリーズ軸受をピストン部材に一体係合すると共に、皿ばねガイドとピストン部材を嵌合により一体構造としたものが開示されている。この技術によれば、組付け時の皿ばねの塑性変形がないものの、皿バネの自由状態の内径が皿ばねガイドの円筒部より大きく構成されているため、組付けた状態では皿ばねの内周端部が皿ばねガイドの円筒部の外周面に接触しない状態になり、皿ばねによる調芯力が減少することがある。また、ピストンがピストン部材と皿ばねガイドに分割した構成であるので、構造が複雑であり、装置のコストが上昇してしまう。   By the way, in Patent Document 2, a disc spring guide is arranged on the side opposite to the cylinder space of the piston member without pressing the disc spring into the annular piston at the time of assembly, and the clutch release bearing is connected to the piston via the disc spring accommodated therein. A disc spring guide and a piston member that are integrally engaged with each other are disclosed. According to this technique, although there is no plastic deformation of the disc spring during assembly, the inner diameter of the disc spring is larger than the cylindrical portion of the disc spring guide. The peripheral end portion is not in contact with the outer peripheral surface of the cylindrical portion of the disc spring guide, and the alignment force by the disc spring may be reduced. Further, since the piston is divided into the piston member and the disc spring guide, the structure is complicated and the cost of the apparatus increases.

本発明の主な課題は、コストを上昇させないで皿バネによる調芯力を発揮させることができる皿バネ組付体を提供することである。   The main subject of this invention is providing the disk spring assembly | attachment body which can exhibit the centering force by a disk spring, without raising cost.

本発明の第１の視点においては、所定の部材に環状部材を一体係合させる皿バネを組付けた皿バネ組付体において、軸方向に延在した取付部を有するとともに、前記取付部の先端外周面に爪部を有し、かつ、前記取付部の末端外周面に段差部を有する所定の部材と、前記取付部の外周に配されるとともに、前記段差部と当接する環状部材と、前記取付部の外周に配されるとともに、内周端部が前記爪部に引っ掛かり、かつ、外周端部が前記環状部材に当接して前記段差部側に付勢する皿バネと、を備え、前記皿バネの内周端部は、前記爪部、及び前記取付部の外周面と圧接し、前記皿バネの外周端部は、前記環状部材と圧接し、前記皿バネは、弾性変形を伴って組み付けられていることを特徴とする。   According to a first aspect of the present invention, in a disc spring assembly in which a disc spring for integrally engaging an annular member with a predetermined member is provided, the disc spring assembly includes an attachment portion extending in the axial direction, A predetermined member having a claw portion on the outer peripheral surface of the tip and a stepped portion on a terminal outer peripheral surface of the mounting portion; an annular member disposed on the outer periphery of the mounting portion and in contact with the stepped portion; A disc spring that is arranged on the outer periphery of the mounting portion, has an inner peripheral end hooked on the claw portion, and an outer peripheral end abuts on the annular member and biases toward the stepped portion; An inner peripheral end portion of the disc spring is in pressure contact with the outer peripheral surface of the claw portion and the mounting portion, an outer peripheral end portion of the disc spring is in press contact with the annular member, and the disc spring is accompanied by elastic deformation. It is characterized by being assembled.

本発明の前記皿バネ組立体において、前記爪部と前記段差部の軸方向の間隔は、前記皿バネの自由時の高さよりも小さく設定されていることが好ましい。   In the disc spring assembly of the present invention, it is preferable that an axial interval between the claw portion and the step portion is set smaller than a free height of the disc spring.

本発明の第２の視点においては、所定の部材に環状部材を一体係合させる皿バネを組付けた皿バネ組付体において、軸方向に延在した取付部を有するとともに、前記取付部の先端外周面に爪部を有する第１の部材と、前記軸方向において前記爪部に所定の距離離間して対向する対向面を有するとともに、前記第１の部材に係合する第２の部材と、前記第１の部材の前記爪部と前記第２の部材の対向面との間に弾撥的に配設される皿バネと、を備え、前記皿バネの内周端部は、前記爪部と前記取付部の外周部と圧接し、前記皿バネの外周端部は、前記対向面に圧接して組み付けられていることを特徴とする。   In a second aspect of the present invention, in a disc spring assembly in which a disc spring for integrally engaging an annular member with a predetermined member is provided, the disc spring assembly includes an attachment portion extending in the axial direction, A first member having a claw portion on the outer peripheral surface of the distal end; a second member having an opposing surface facing the claw portion at a predetermined distance in the axial direction; and a second member engaged with the first member. A disc spring elastically disposed between the claw portion of the first member and the opposing surface of the second member, and an inner peripheral end portion of the disc spring includes the claw And an outer peripheral end of the disc spring are assembled in pressure contact with the opposing surface.

本発明によれば、皿バネの内周端部及び外周端部が軸方向で接するとともに、皿バネの内周端部が径方向で接するように、皿バネの自由高さ、皿バネの自由内径、爪部と段差部の軸方向の間隔（皿バネの組付時高さ）、爪部の外周面の径（皿バネの組付時最大内径）、及び取付部（爪部を除く）の外周面の径（皿バネの組付時内径）を設定することにより、組付状態の皿バネの反力が安定した状態となり、皿バネによる調芯力を安定化させることができる。また、所定の部材が取付部で分割した構成とはなっていないので装置のコストが上昇することがない。   According to the present invention, the free height of the disc spring and the free spring of the disc spring are such that the inner peripheral end portion and the outer peripheral end portion of the disc spring are in contact in the axial direction, and the inner peripheral end portion of the disc spring is in contact in the radial direction. Inner diameter, axial distance between claw and step (height when disc spring is assembled), outer diameter of claw (maximum inner diameter when disc spring is assembled), and attachment (excluding claw) By setting the diameter of the outer peripheral surface (the inner diameter when the disc spring is assembled), the reaction force of the disc spring in the assembled state becomes stable, and the alignment force by the disc spring can be stabilized. In addition, since the predetermined member is not divided by the attachment portion, the cost of the apparatus does not increase.

本発明の実施形態１に係る皿バネ組付体では、軸方向に延在した取付部（図３の６ａ）を有するとともに、前記取付部（図３の６ａ）の先端外周面に爪部（図３の６ｂ）を有し、かつ、前記取付部（図３の６ａ）の末端外周面に段差部（図３の６ｃ）を有する所定の部材（図３の６）と、前記取付部（図３の６ａ）の外周に配されるとともに、前記段差部（図３の６ｃ）と当接する環状部材（図３の５ａ）と、前記取付部（図３の６ａ）の外周に配されるとともに、内周端部が前記爪部（図３の６ｂ）に引っ掛かり、かつ、外周端部が前記環状部材（図３の５ａ）に当接して前記段差部（図３の６ｃ）側に付勢する皿バネ（図３の８）と、を備え、前記皿バネ（図３の８）の内周端部は、前記爪部（図３の６ｂ）、及び前記取付部（図３の６ａ）の外周面と圧接し、前記皿バネ（図３の８）の外周端部は、前記環状部材（図３の５ａ）と圧接し、前記皿バネ（図３の８）は、弾性変形を伴って組み付けられている。   The disc spring assembly according to Embodiment 1 of the present invention has an attachment portion (6a in FIG. 3) extending in the axial direction, and a claw portion (6a in FIG. 3) on the distal end outer peripheral surface of the attachment portion (6a in FIG. 3). 3b and a predetermined member (6 in FIG. 3) having a stepped portion (6c in FIG. 3) on the outer peripheral surface of the end of the mounting portion (6a in FIG. 3), and the mounting portion (6b in FIG. 3). 3 is arranged on the outer periphery of 6a), and is also arranged on the outer periphery of the annular member (5a in FIG. 3) that contacts the stepped portion (6c in FIG. 3) and the mounting portion (6a in FIG. 3). At the same time, the inner peripheral end is hooked on the claw portion (6b in FIG. 3), and the outer peripheral end abuts on the annular member (5a in FIG. 3) and is attached to the stepped portion (6c in FIG. 3). A disc spring (8 in FIG. 3), and the inner peripheral end of the disc spring (8 in FIG. 3) is the claw portion (6b in FIG. 3) and the mounting portion (6 in FIG. 3). ), The outer peripheral end of the disc spring (8 in FIG. 3) is in press contact with the annular member (5a in FIG. 3), and the disc spring (8 in FIG. 3) is elastically deformed. It is assembled with it.

本発明の実施形態２に係る皿バネ組付体では、軸方向に延在した取付部（図３の６ａ）を有するとともに、前記取付部（図３の６ａ）の先端外周面に爪部（図３の６ｂ）を有する第１の部材（図３の６）と、前記軸方向において前記爪部（図３の６ｂ）に所定の距離離間して対向する対向面を有するとともに、前記第１の部材（図３の６）に係合する第２の部材（図３の５ａ）と、前記第１の部材（図３の６）の前記爪部（図３の６ｂ）と前記第２の部材（図３の５ａ）の対向面との間に弾撥的に配設される皿バネ（図３の８）と、を備え、前記皿バネ（図３の８）の内周端部は、前記爪部（図３の６ｂ）と前記取付部（図３の６ａ）の外周部と圧接し、前記皿バネ（図３の８）の外周端部は、前記対向面に圧接して組み付けられている。   The disc spring assembly according to the second embodiment of the present invention has an attachment portion (6a in FIG. 3) extending in the axial direction, and a claw portion (6a in FIG. 3) on the tip outer peripheral surface of the attachment portion (6a in FIG. 3). 3b) and a first member (6b of FIG. 3) having a facing surface facing the claw portion (6b of FIG. 3) at a predetermined distance in the axial direction, and the first member The second member (5a in FIG. 3) that engages with the member (6 in FIG. 3), the claw portion (6b in FIG. 3) of the first member (6 in FIG. 3), and the second member A disc spring (8 in FIG. 3) elastically disposed between the opposing surfaces of the members (5a in FIG. 3), and an inner peripheral end of the disc spring (8 in FIG. 3) The claw portion (6b in FIG. 3) and the outer peripheral portion of the mounting portion (6a in FIG. 3) are pressed against each other, and the outer peripheral end portion of the disc spring (8 in FIG. 3) is pressed against the opposing surface and assembled. It has been.

本発明の実施例１に係る皿バネ組付体について、油圧式クラッチレリーズ装置を例に図面を用いて説明する。図１は、本発明の実施例１に係る皿バネ組付体を含む油圧式クラッチレリーズ装置の構成を模式的に示した断面図である。図２は、本発明の実施例１に係る皿バネ組付体における皿バネの自由状態（組付け前）の構成を模式的に示した（Ａ）平面図、及び（Ｂ）断面図である。図３は、本発明の実施例１に係る皿バネ組付体の構成を模式的に示した断面図である。図４は、本発明の実施例１に係る皿バネ組付体における皿バネの付勢方向を模式的に示した模式図である。   The disc spring assembly according to the first embodiment of the present invention will be described with reference to the drawings, taking a hydraulic clutch release device as an example. 1 is a cross-sectional view schematically showing a configuration of a hydraulic clutch release device including a disc spring assembly according to Embodiment 1 of the present invention. 2A is a plan view and FIG. 2B is a cross-sectional view schematically showing a configuration of a disc spring in a free state (before assembly) in the disc spring assembly according to the first embodiment of the present invention. . FIG. 3 is a cross-sectional view schematically showing the configuration of the disc spring assembly according to the first embodiment of the present invention. FIG. 4 is a schematic diagram schematically showing a biasing direction of the disc spring in the disc spring assembly according to the first embodiment of the present invention.

図１を参照すると、油圧式クラッチレリーズ装置は、内側ハウジング１と外側ハウジング２と第２環状ピストン７とによって内側ハウジング１と外側ハウジング２との間に油室４を形成し、油室４内の油圧によって環状ピストン６、７、及びレリーズベアリング５を回転軸の軸方向へ移動してクラッチ（図示せず）を遮断状態にする装置である。油圧式クラッチレリーズ装置は、内側ハウジング１と、外側ハウジング２と、シール３と、油室４と、レリーズベアリング５と、第１環状ピストン６と、第２環状ピストン７と、皿バネ８と、リターンスプリング９と、シート部材１０と、カバー部材１１と、止め輪１２と、シール１３と、ストッパ部材１４と、を有する。   Referring to FIG. 1, in the hydraulic clutch release device, an inner chamber 1, an outer housing 2, and a second annular piston 7 form an oil chamber 4 between the inner housing 1 and the outer housing 2. This is a device that moves the annular pistons 6 and 7 and the release bearing 5 in the axial direction of the rotary shaft by the hydraulic pressure of the clutch to disengage the clutch (not shown). The hydraulic clutch release device includes an inner housing 1, an outer housing 2, a seal 3, an oil chamber 4, a release bearing 5, a first annular piston 6, a second annular piston 7, a disc spring 8, A return spring 9, a seat member 10, a cover member 11, a retaining ring 12, a seal 13, and a stopper member 14 are included.

内側ハウジング１は、環状（ドラム状、筒状）の部材であり、シリンダ室の一部となる。内側ハウジング１は、筒状部１ａと、フランジ部１ｂと、を有する。筒状部１ａは、変速機（図示せず）の入力軸（図示せず）を包囲する部分である。フランジ部１ｂは、筒状部１ａの一端から外周方向に延在した部分である。   The inner housing 1 is an annular (drum-shaped, cylindrical) member, and becomes a part of the cylinder chamber. The inner housing 1 has a cylindrical portion 1a and a flange portion 1b. The cylindrical part 1a is a part surrounding an input shaft (not shown) of a transmission (not shown). The flange portion 1b is a portion extending in the outer peripheral direction from one end of the tubular portion 1a.

外側ハウジング２は、所定間隔をおいて内側ハウジング１を包囲するように配され、シリンダ室の一部となる。外側ハウジング２は、油ポート２ａと、取付フランジ２ｂと、段差部２ｃと、を有する。油ポート２ａは、クラッチマスタシリンダ（図示せず）等から供給された圧油を油室４に供給する油路となる部分である。取付フランジ２ｂは、変速機等に取り付けるためのフランジ形状部分である。段差部２ｃは、外側ハウジング２のフランジ部１ｂ側の面に形成された凹部であり、油室４の外周にて環状に形成されている。段差部２ｃは、油ポート２ａからの圧油を油室４に供給する油路となる。   The outer housing 2 is arranged so as to surround the inner housing 1 at a predetermined interval, and becomes a part of the cylinder chamber. The outer housing 2 has an oil port 2a, a mounting flange 2b, and a step portion 2c. The oil port 2 a is a portion serving as an oil passage for supplying pressure oil supplied from a clutch master cylinder (not shown) or the like to the oil chamber 4. The attachment flange 2b is a flange-shaped portion for attachment to a transmission or the like. The step portion 2 c is a recess formed on the surface of the outer housing 2 on the flange portion 1 b side, and is formed in an annular shape on the outer periphery of the oil chamber 4. The step portion 2 c serves as an oil passage for supplying the pressure oil from the oil port 2 a to the oil chamber 4.

シール３は、弾性材料よりなり、油室４を密封する環状のシール部材である。シール３は、内側ハウジング１と外側ハウジング２の間に配され、第２環状ピストン７の凹部７ａに装着されている。   The seal 3 is an annular seal member made of an elastic material and sealing the oil chamber 4. The seal 3 is disposed between the inner housing 1 and the outer housing 2 and is attached to the recess 7 a of the second annular piston 7.

油室４は、内側ハウジング１、外側ハウジング２、及び第２環状ピストン７に囲まれた環状のシリンダ室である。油室４は、段差部２ｃとフランジ部１ｂの間の油路、及び油ポート２ａを介してクラッチマスタシリンダ（図示せず）等に接続されている。   The oil chamber 4 is an annular cylinder chamber surrounded by the inner housing 1, the outer housing 2, and the second annular piston 7. The oil chamber 4 is connected to a clutch master cylinder (not shown) or the like through an oil passage between the step portion 2c and the flange portion 1b, and an oil port 2a.

レリーズベアリング５は、皿バネ８によって第１環状ピストン６に調芯可能に取り付けられたボールベアリングである。レリーズベアリング５の内輪５ａは、内周部分にて皿バネ８によって第１環状ピストン６に調芯可能に取り付けられた非回転の環状部材であり、皿バネ８の外周端部と当接している。内輪５ａは、外周部分のリターンスプリング９側の面にてシート部材１０を介してリターンスプリング９の付勢力を受けている。内輪５ａの内周端部は、第１環状ピストン６の取付部６ａの外周面と所定のクリアランス（少なくとも爪部６ｂが挿通可能なクリアランス）を介して配される。レリーズベアリング５の外輪５ｂは、ボールを介して内輪５ａに回動可能に支持されており、クラッチ側（図１の右側）の端部にてダイヤフラムスプリング（図示せず）と常時接合している。したがって、外輪５ｂは、ダイヤフラムスプリング（図示せず）と一体的に回転する。なお、ダイヤフラムスプリング（図示せず）は、プレッシャプレート（図示せず）を介してクラッチディスク（図示せず）をフライホイール（図示せず）に圧接させる。   The release bearing 5 is a ball bearing attached to the first annular piston 6 by a disc spring 8 so as to be aligned. The inner ring 5 a of the release bearing 5 is a non-rotating annular member that is attached to the first annular piston 6 by a disc spring 8 at the inner peripheral portion so as to be aligned, and is in contact with the outer peripheral end of the disc spring 8. . The inner ring 5a receives the biasing force of the return spring 9 via the seat member 10 on the surface of the outer peripheral portion on the return spring 9 side. The inner peripheral end portion of the inner ring 5a is arranged with a predetermined clearance (at least a clearance through which the claw portion 6b can be inserted) from the outer peripheral surface of the mounting portion 6a of the first annular piston 6. The outer ring 5b of the release bearing 5 is rotatably supported by the inner ring 5a via a ball, and is always joined to a diaphragm spring (not shown) at the end on the clutch side (right side in FIG. 1). . Therefore, the outer ring 5b rotates integrally with a diaphragm spring (not shown). A diaphragm spring (not shown) presses a clutch disk (not shown) to a flywheel (not shown) via a pressure plate (not shown).

第１環状ピストン６は、内側ハウジング１と外側ハウジング２の間において第２環状ピストン７の摺動により軸方向（図１の左右方向）に摺動可能に作動する筒状部材である。第１環状ピストン６は、外側ハウジング２に収容されない部位にレリーズベアリング５を取り付けるための取付部６ａを有する。取付部６ａは、先端外周面に皿バネ８の内周端部を引掛けるための爪部６ｂを有し、末端外周面にレリーズベアリング５の内輪５ａの座部となる段差部６ｃを有する。第１環状ピストン６は、油室４側の端部にて第２環状ピストン７と接離可能に当接している。第１環状ピストン６の取付部６ａの詳細は、後述する。   The first annular piston 6 is a cylindrical member that is slidable in the axial direction (left-right direction in FIG. 1) by sliding the second annular piston 7 between the inner housing 1 and the outer housing 2. The first annular piston 6 has an attachment portion 6 a for attaching the release bearing 5 to a portion that is not accommodated in the outer housing 2. The attachment portion 6a has a claw portion 6b for hooking the inner peripheral end portion of the disc spring 8 on the tip outer peripheral surface, and has a step portion 6c serving as a seat portion for the inner ring 5a of the release bearing 5 on the terminal outer peripheral surface. The first annular piston 6 is in contact with the second annular piston 7 at the end on the oil chamber 4 side so as to be able to contact and separate. Details of the mounting portion 6a of the first annular piston 6 will be described later.

第２環状ピストン７は、内側ハウジング１と外側ハウジング２の間において油圧により軸方向（図１の左右方向）に摺動可能に作動する部材である。第２環状ピストン７は、油室４側の端部にシール３を装着するための凹部７ａを有する。第２環状ピストン７は、クラッチ側（図１の右側）の端部にて第１環状ピストン６と接離可能に当接している。   The second annular piston 7 is a member that is slidable in the axial direction (left-right direction in FIG. 1) by hydraulic pressure between the inner housing 1 and the outer housing 2. The second annular piston 7 has a recess 7a for mounting the seal 3 on the end portion on the oil chamber 4 side. The second annular piston 7 is in contact with the first annular piston 6 at the end on the clutch side (right side in FIG. 1) so as to be able to contact and separate.

皿バネ８は、第１環状ピストン６の取付部６ａにレリーズベアリング５の内輪５ａを調芯可能に取り付けるためのばね弾性を有する皿状の部材である。皿バネ８は、外周部に環状に形成された外周環状部８ａを有し、外周環状部８ａの内周端部から内周側に突出した複数の内周凸部８ｂを有し、隣り合う内周凸部８ｂ間に凹部８ｃを有する（図２参照）。外周環状部８ａの外周端部は、レリーズベアリング５の内輪５ａを第１環状ピストン６の段差部６ｃに向けて付勢する（図４参照）。内周凸部８ｂは、所定の位置で曲った部分を有する。内周凸部８ｂの内周端部は、第１環状ピストン６の爪部６ｂに引っ掛かり、爪部６ｂを第１環状ピストン６の取付部６ａの先端側に付勢するとともに、取付部６ａの外周面を内周側に付勢する（図４参照）。皿バネ８は、皿バネ８を組付けた時に、皿バネ８の組付高さｈが変動しても安定した反力を得ることを要する。皿バネ８の詳細については、後述する。   The disc spring 8 is a plate-like member having spring elasticity for attaching the inner ring 5a of the release bearing 5 to the attachment portion 6a of the first annular piston 6 so that the inner ring 5a can be aligned. The disc spring 8 has an outer peripheral annular portion 8a formed in an annular shape on the outer peripheral portion, has a plurality of inner peripheral convex portions 8b protruding from the inner peripheral end portion of the outer peripheral annular portion 8a toward the inner peripheral side, and adjacent inner peripheral convex portions. A recess 8c is provided between 8b (see FIG. 2). The outer peripheral end of the outer peripheral annular portion 8a biases the inner ring 5a of the release bearing 5 toward the step portion 6c of the first annular piston 6 (see FIG. 4). The inner peripheral convex portion 8b has a bent portion at a predetermined position. The inner peripheral end portion of the inner peripheral convex portion 8b is hooked on the claw portion 6b of the first annular piston 6 and urges the claw portion 6b toward the distal end side of the attachment portion 6a of the first annular piston 6, and the outer peripheral surface of the attachment portion 6a. Is urged toward the inner peripheral side (see FIG. 4). When the disc spring 8 is assembled, the disc spring 8 needs to obtain a stable reaction force even if the assembly height h of the disc spring 8 varies. Details of the disc spring 8 will be described later.

リターンスプリング９は、入力軸（図示せず）の軸方向（図１の左右方向）であってシート部材１０とカバー部材１１のシート部１１ａとの間に介在している。リターンスプリング９は、シート部材１０を介してレリーズベアリング５をダイヤフラムスプリング（図示せず）側に付勢している。   The return spring 9 is interposed between the seat member 10 and the seat portion 11a of the cover member 11 in the axial direction (left-right direction in FIG. 1) of an input shaft (not shown). The return spring 9 biases the release bearing 5 toward the diaphragm spring (not shown) via the seat member 10.

シート部材１０は、リターンスプリング９の一端を支持するための部材であり、レリーズベアリング５の内輪５ａに取り付けられている。   The seat member 10 is a member for supporting one end of the return spring 9, and is attached to the inner ring 5 a of the release bearing 5.

カバー部材１１は、リターンスプリング９の外周をカバーする円筒状の部材である。カバー部材１１は、環状ピストン６、７が油室４側にスライドしたときにもレリーズベアリング５と抵触しないように設定されている。カバー部材１１は、変速機側（図１の左側）の端部にて内周側に延在したシート部１１ａを有する。シート部１１ａは、リターンスプリング９の他端を支持し、外側ハウジング２に当接している。   The cover member 11 is a cylindrical member that covers the outer periphery of the return spring 9. The cover member 11 is set so as not to interfere with the release bearing 5 even when the annular pistons 6 and 7 slide to the oil chamber 4 side. The cover member 11 has a seat portion 11a that extends to the inner peripheral side at an end portion on the transmission side (left side in FIG. 1). The seat portion 11 a supports the other end of the return spring 9 and is in contact with the outer housing 2.

止め輪１２は、環状ピストン６、７のクラッチ側（図１の右側）へのスライドを規制する環状部材である。止め輪１２は、内側ハウジング１の外周面のクラッチ側（図１の右側）の端部の近傍に形成された溝に取り付けられている。   The retaining ring 12 is an annular member that restricts the sliding of the annular pistons 6 and 7 to the clutch side (right side in FIG. 1). The retaining ring 12 is attached to a groove formed in the vicinity of the end of the outer peripheral surface of the inner housing 1 on the clutch side (right side in FIG. 1).

シール１３は、内側ハウジング１のフランジ部１ｂと外側ハウジング２との接合面を封止するための弾性材料よりなる環状部材である。シール１３は、油室４及び油ポート２ａよりも外周側に配されている。   The seal 13 is an annular member made of an elastic material for sealing the joint surface between the flange portion 1 b of the inner housing 1 and the outer housing 2. The seal 13 is disposed on the outer peripheral side of the oil chamber 4 and the oil port 2a.

ストッパ部材１４は、シール３の変速機側（図１の左側）へのスライドを規制する環状部材である。ストッパ部材１４は、エンジン（図示せず）のクランクシャフト（図示せず）によってもたらされる軸方向振動の油圧系への伝播遮断のためにピストンを完全分離した際に、シール３が段差部２ｃとフランジ部１ｂの間の油路で傷付かないようにするためのものである。ストッパ部材１４は、内側ハウジング１の円筒部１ａの外周にて、油室４のフランジ部１ｂ近傍の部分から段差部２ｃとフランジ部１ｂの間の油路において、回動可能に配置されている。   The stopper member 14 is an annular member that restricts sliding of the seal 3 toward the transmission side (left side in FIG. 1). When the piston is completely separated for blocking the propagation of the axial vibration caused by the crankshaft (not shown) of the engine (not shown) to the hydraulic system, the stopper member 14 is separated from the step 2c. This is to prevent the oil passage between the flange portions 1b from being damaged. The stopper member 14 is rotatably disposed on the outer periphery of the cylindrical portion 1a of the inner housing 1 in the oil passage between the step portion 2c and the flange portion 1b from a portion near the flange portion 1b of the oil chamber 4. .

次に、本発明の実施例１に係る皿バネ組付体における皿バネの特性について図面を用いて説明する。図５は、本発明の実施例１に係る皿バネ組付体における皿バネのひずみ−応力特性を示したグラフである。図６は、本発明の実施例１に係る皿バネ組付体における皿バネの組付時高さ−調芯荷重特性を示したグラフである。   Next, characteristics of the disc spring in the disc spring assembly according to the first embodiment of the present invention will be described with reference to the drawings. FIG. 5 is a graph showing strain-stress characteristics of a disc spring in the disc spring assembly according to the first embodiment of the present invention. FIG. 6 is a graph showing the height-alignment load characteristic when the disc spring is assembled in the disc spring assembly according to the first embodiment of the present invention.

皿バネ８の組付けの過程において、皿バネ８の内径の変化に着目すると、爪部６ｂを通過する過程で自由状態の自由時内径ｄｗ（図２（Ｂ）参照）から組付時最大内径ｄ１（図３参照）となり、爪部６ｂを超えて取付部６ａの外周面と当接する過程で組付時最大内径ｄ１から片側変動量ΔＬ（図３参照）の２倍だけ戻り、組付時直径ｄ２（図３参照）となる。皿バネ８は、爪部６ｂを通過する過程で主に内周凸部８ｂの曲った部分で塑性変形を伴い、爪部６ｂを超えて取付部６ａの外周面と当接するまでの過程で塑性変形した状態で片側変動量ΔＬの２倍だけ戻る。組付時最大内径ｄ１での塑性変形量は皿バネ８の組付時高さｈ（図３参照）により変動するが、片側変動量ΔＬが決まっていれば、図５のように反力Ｆ（弾性力）はほぼ同じで安定し、所定の組付時高さｈの範囲で、図６のように皿バネ８の調芯荷重が安定する。 Focusing on the change in the inner diameter of the disc spring 8 in the process of assembling the disc spring 8, the maximum at the time of assembly from the free inner diameter d w (see FIG. 2B) in the free state in the process of passing through the claw portion 6b. It becomes an inner diameter d 1 (see FIG. 3), and in the process of coming into contact with the outer peripheral surface of the mounting portion 6a beyond the claw portion 6b, it returns from the maximum inner diameter d 1 during assembly by twice the one-side variation ΔL (see FIG. 3) The diameter d 2 (see FIG. 3) when assembled. The disc spring 8 is plastically deformed mainly at the bent portion of the inner peripheral convex portion 8b in the process of passing the claw portion 6b, and is plastically deformed in the process of exceeding the claw portion 6b and coming into contact with the outer peripheral surface of the mounting portion 6a. In this state, it returns by twice the one-side fluctuation amount ΔL. Plastic deformation of at assembly time of the maximum inner diameter d 1 varies by assembling at height of the conical spring 8 h (see FIG. 3), if the decided one variation [Delta] L, reaction force as in Fig. 5 F (elastic force) is substantially the same and stable, and the centering load of the disc spring 8 is stabilized as shown in FIG.

なお、組付時高さｈを高くした場合、皿バネ８の内周端部及び外周端部が軸方向で接していても、内周端部が径方向で接していない領域（内径非接触領域）では、組付時高さｈが高くなるにつれて皿バネ８の調芯荷重の減少が急になる（図６参照）、一方、組付時高さｈを低くした場合、皿バネ８の内周端部及び外周端部が軸方向で接し、かつ、内周端部が径方向で接していても、皿バネ８の塑性変形過大領域では、組付時高さｈが低くなるにつれて皿バネ８の調芯荷重の減少が急になる（図６参照）。   When the height h during assembly is increased, even if the inner peripheral end and the outer peripheral end of the disc spring 8 are in contact in the axial direction, the inner peripheral end is not in contact in the radial direction (inner diameter non-contact In the region), as the height h during assembly increases, the centering load of the disc spring 8 decreases sharply (see FIG. 6). On the other hand, when the height h during assembly decreases, the disc spring 8 Even if the inner peripheral end and the outer peripheral end are in contact in the axial direction, and the inner peripheral end is in contact in the radial direction, in the excessively plastic deformation region of the disc spring 8, as the height h during assembly decreases, The centering load of the spring 8 is suddenly reduced (see FIG. 6).

以上のことから、皿バネ８は、内周端部及び外周端部が軸方向で接するとともに、内周端部が径方向で接し、かつ、適度な塑性変形領域内（弾性変形を伴う安定領域）で、組付状態の調芯加重が安定し、反力が安定する。このように安定した状態は、皿バネ８の自由高さｈｗ、皿バネ８の自由内径ｄｗ、皿バネ８の組付時高さｈ、皿バネ８の組付時内径ｄ１、及び皿バネ８の組付時内径ｄ２の組み合わせにより決定される。例えば、皿バネ８の自由高さｈｗ＝４．７ｍｍ、皿バネ８の自由内径ｄｗ＝３４．０５ｍｍ、皿バネ８の組付時高さｈ＝３．６、皿バネ８の組付時最大内径ｄ１＝３４．２ｍｍ、皿バネ８の組付時内径ｄ２＝３３．２ｍｍとすることで、皿バネ８の内周端部及び外周端部が軸方向で接するとともに、皿バネ８の内周端部が径方向で接し、かつ、塑性変形を伴わない領域に入り、組付状態の調芯加重が安定し、反力が安定した状態を達成することができる。 From the above, the disc spring 8 has an inner peripheral end and an outer peripheral end in contact with each other in the axial direction, and an inner peripheral end in contact with each other in the radial direction, and within an appropriate plastic deformation region (a stable region with elastic deformation). ), The alignment load in the assembled state is stabilized, and the reaction force is stabilized. In this stable state, the free height h w of the disc spring 8, the free inner diameter d w of the disc spring 8, the height h when the disc spring 8 is assembled, the inner diameter d 1 when the disc spring 8 is assembled, and is determined by a combination of the assembly when the inner diameter d 2 of the disc spring 8. For example, the free height h w = 4.7 mm of the disc spring 8, the free inner diameter d w = 34.05 mm of the disc spring 8, the height h = 3.6 when the disc spring 8 is assembled, and the assembly of the disc spring 8 The maximum inner diameter d 1 = 34.2 mm and the inner diameter d 2 = 33.2 mm when the disc spring 8 is assembled, so that the inner and outer peripheral ends of the disc spring 8 are in axial contact with each other, and the disc spring The inner peripheral end of 8 is in contact in the radial direction and enters a region without plastic deformation, the alignment load in the assembled state is stable, and the reaction force is stable.

実施例１によれば、皿バネ８の内周端部及び外周端部が軸方向で接するとともに、皿バネ８の内周端部が径方向で接し、かつ、適度な塑性変形領域となるように、皿バネ８の自由高さｈｗ、皿バネ８の自由内径ｄｗ、皿バネ８の組付時高さｈ（第１環状ピストン６の爪部６ｂと段差部６ｃの軸方向の間隔）、皿バネ８の組付時最大内径ｄ１（第１環状ピストン６の爪部６ｂの外周面の径）、及び皿バネ８の組付時内径ｄ２（第１環状ピストン６の取付部６ａ（爪部６ｂを除く）の外周面の径）を設定することにより、組付状態の皿バネ８の反力が安定した状態となり、皿バネによる調芯力を安定化させることができる。また、第１環状ピストン６が取付部６ａで分割した構成ではないので装置のコストが上昇することがない。 According to the first embodiment, the inner peripheral end portion and the outer peripheral end portion of the disc spring 8 are in contact in the axial direction, and the inner peripheral end portion of the disc spring 8 is in contact in the radial direction, and an appropriate plastic deformation region is obtained. The free height h w of the disc spring 8, the free inner diameter d w of the disc spring 8, and the height h when the disc spring 8 is assembled (the distance between the claw portion 6 b of the first annular piston 6 and the step portion 6 c in the axial direction) ), The maximum inner diameter d 1 (diameter of the outer peripheral surface of the claw portion 6b of the first annular piston 6) when the disc spring 8 is assembled, and the inner diameter d 2 (attachment portion of the first annular piston 6) when the disc spring 8 is assembled. By setting 6a (the diameter of the outer peripheral surface of the claw portion 6b), the reaction force of the disc spring 8 in the assembled state becomes stable, and the alignment force by the disc spring can be stabilized. Moreover, since the 1st annular piston 6 is not the structure divided | segmented by the attaching part 6a, the cost of an apparatus does not rise.

本発明の実施例１に係る皿バネ組付体を含む油圧式クラッチレリーズ装置の構成を模式的に示した断面図である。It is sectional drawing which showed typically the structure of the hydraulic clutch release apparatus containing the disc spring assembly which concerns on Example 1 of this invention. 本発明の実施例１に係る皿バネ組付体における皿バネの自由状態（組付け前）の構成を模式的に示した（Ａ）平面図、及び（Ｂ）断面図である。It is the (A) top view and (B) sectional view which showed typically the structure of the free state (before assembly | attachment) of the disc spring in the disc spring assembly | attachment body which concerns on Example 1 of this invention. 本発明の実施例１に係る皿バネ組付体の構成を模式的に示した断面図である。It is sectional drawing which showed typically the structure of the disk spring assembly | attachment body which concerns on Example 1 of this invention. 本発明の実施例１に係る皿バネ組付体における皿バネの付勢方向を模式的に示した模式図である。It is the schematic diagram which showed typically the urging | biasing direction of the disc spring in the disc spring assembly which concerns on Example 1 of this invention. 本発明の実施例１に係る皿バネ組付体における皿バネのひずみ−応力特性を示したグラフである。It is the graph which showed the distortion-stress characteristic of the disc spring in the disc spring assembly | attachment body which concerns on Example 1 of this invention. 本発明の実施例１に係る皿バネ組付体における皿バネの組付時高さ−調芯荷重特性を示したグラフである。It is the graph which showed the height-alignment load characteristic at the time of the assembly | attachment of the disc spring in the disc spring assembly which concerns on Example 1 of this invention.

符号の説明Explanation of symbols

１ 内側ハウジング
１ａ 筒状部
１ｂ フランジ部
２ 外側ハウジング
２ａ 油ポート
２ｂ 取付フランジ
２ｃ 段差部
３ シール
４ 油室（シリンダ室）
５ レリーズベアリング
５ａ 内輪（環状部材、第２の部材）
５ｂ 外輪
６ 第１環状ピストン（所定の部材、第１の部材）
６ａ 取付部
６ｂ 爪部
６ｃ 段差部
７ 第２環状ピストン
７ａ 凹部
８ 皿バネ
８ａ 外周環状部
８ｂ 内周凸部
８ｃ 凹部
９ リターンスプリング
１０ シート部材
１１ カバー部材
１１ａ シート部
１２ 止め輪
１３ シール
１４ ストッパ部材 DESCRIPTION OF SYMBOLS 1 Inner housing 1a Tubular part 1b Flange part 2 Outer housing 2a Oil port 2b Mounting flange 2c Step part 3 Seal 4 Oil chamber (cylinder chamber)
5 Release bearing 5a Inner ring (annular member, second member)
5b Outer ring 6 First annular piston (predetermined member, first member)
6a Mounting portion 6b Claw portion 6c Stepped portion 7 Second annular piston 7a Recessed portion 8 Belleville spring 8a Outer circumferential annular portion 8b Inner circumferential convex portion 8c Recessed portion 9 Return spring 10 Seat member 11 Cover member 11a Seat portion 12 Retaining ring 13 Seal 14 Stopper member

Claims (3)

軸方向に延在した取付部を有するとともに、前記取付部の先端外周面に爪部を有し、かつ、前記取付部の末端外周面に段差部を有する所定の部材と、
前記取付部の外周に配されるとともに、前記段差部と当接する環状部材と、
前記取付部の外周に配されるとともに、内周端部が前記爪部に引っ掛かり、かつ、外周端部が前記環状部材に当接して前記段差部側に付勢する皿バネと、
を備え、
前記皿バネの内周端部は、前記爪部、及び前記取付部の外周面と圧接し、
前記皿バネの外周端部は、前記環状部材と圧接し、
前記皿バネは、弾性変形を伴って組み付けられていることを特徴とする皿バネ組立体。 A predetermined member having an attachment portion extending in the axial direction, a claw portion on a distal outer peripheral surface of the attachment portion, and a stepped portion on a distal outer peripheral surface of the attachment portion;
An annular member disposed on the outer periphery of the mounting portion and in contact with the stepped portion;
A disc spring that is arranged on the outer periphery of the mounting portion, the inner peripheral end is hooked on the claw portion, and the outer peripheral end abuts on the annular member and is biased toward the stepped portion.
With
The inner peripheral end of the disc spring is in pressure contact with the claw portion and the outer peripheral surface of the mounting portion,
The outer peripheral end of the disc spring is in pressure contact with the annular member,
The disc spring assembly is characterized in that the disc spring is assembled with elastic deformation. 前記爪部と前記段差部の軸方向の間隔は、前記皿バネの自由時の高さよりも小さく設定されていることを特徴とする請求項１記載の皿バネ組立体。   The disc spring assembly according to claim 1, wherein an interval between the claw portion and the stepped portion in the axial direction is set smaller than a free height of the disc spring. 軸方向に延在した取付部を有するとともに、前記取付部の先端外周面に爪部を有する第１の部材と、
前記軸方向において前記爪部に所定の距離離間して対向する対向面を有するとともに、前記第１の部材に係合する第２の部材と、
前記第１の部材の前記爪部と前記第２の部材の対向面との間に弾撥的に配設される皿バネと、
を備え、
前記皿バネの内周端部は、前記爪部と前記取付部の外周部と圧接し、
前記皿バネの外周端部は、前記対向面に圧接して組み付けられていることを特徴とする皿バネ組立体。 A first member having an attachment portion extending in the axial direction and having a claw portion on the outer peripheral surface of the tip of the attachment portion;
A second member that engages with the first member, and has an opposing surface that is opposed to the claw portion at a predetermined distance in the axial direction;
A disc spring elastically disposed between the claw portion of the first member and the opposing surface of the second member;
With
The inner peripheral end of the disc spring is in pressure contact with the outer peripheral portion of the claw portion and the attachment portion,
The disc spring assembly is characterized in that an outer peripheral end portion of the disc spring is assembled in pressure contact with the facing surface.
JP2008256359A 2008-10-01 2008-10-01 Disc spring assembly Pending JP2010084892A (en)

Priority Applications (1)

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Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
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Publications (1)

Publication Number Publication Date
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Family

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Country Link
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101600923B1 (en) * 2014-09-19 2016-03-08 주식회사 인팩 Clutch actuator
WO2022085338A1 (en) * 2020-10-22 2022-04-28 株式会社デンソー Gas sensor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59197624A (en) * 1983-04-15 1984-11-09 ヴァレオ Method of assembling clutch thrust bearing for automobile and clutch thrust bearing
JPH11190363A (en) * 1997-12-26 1999-07-13 Ntn Corp Self-aligning type clutch release bearing device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59197624A (en) * 1983-04-15 1984-11-09 ヴァレオ Method of assembling clutch thrust bearing for automobile and clutch thrust bearing
JPH11190363A (en) * 1997-12-26 1999-07-13 Ntn Corp Self-aligning type clutch release bearing device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101600923B1 (en) * 2014-09-19 2016-03-08 주식회사 인팩 Clutch actuator
WO2022085338A1 (en) * 2020-10-22 2022-04-28 株式会社デンソー Gas sensor
JP2022068601A (en) * 2020-10-22 2022-05-10 株式会社デンソー Gas sensor

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