JP2009168178A - Hydraulic clutch release bearing device - Google Patents

Hydraulic clutch release bearing device Download PDF

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JP2009168178A
JP2009168178A JP2008007928A JP2008007928A JP2009168178A JP 2009168178 A JP2009168178 A JP 2009168178A JP 2008007928 A JP2008007928 A JP 2008007928A JP 2008007928 A JP2008007928 A JP 2008007928A JP 2009168178 A JP2009168178 A JP 2009168178A
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cylindrical body
flange
cylindrical
release bearing
clutch release
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JP5018498B2 (en
JP2009168178A5 (en
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Akiyuki Suzuki
章之 鈴木
孝 ▲すぎ▼本
Takashi Sugimoto
Motoji Kawamura
基司 河村
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JTEKT Corp
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JTEKT Corp
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    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging bearing

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic clutch release bearing device miniaturizing the whole device by reducing the outside diameter dimension of the cylindrical body of a cover member. <P>SOLUTION: The flange body 60 and cylindrical body 51 of the cover member 50 are composed of separate components. The cylindrical body 51 integrally has a cylindrical barrel portion 52 formed into a cylindrical shape by a metal plate thinner than the flange body 60 and an annular end wall portion 54 bent radially inward from one edge of the cylindrical barrel body 52. The flange body 60 and an outer ring 31 are sequentially pressure-fitted and fixed into the cylindrical body 51, and also the cylindrical body 51, flange body 60 and outer ring 31 are integrated with each other by abutting one side of the flange body 60 on the annular end wall portion 54 and abutting one end surface of the outer ring 31 on the other side of the flange body 60. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は、油圧によって作動される環状ピストンとダイヤフラムスプリングとの間に配設される油圧式クラッチレリーズ軸受装置に関する。   The present invention relates to a hydraulic clutch release bearing device disposed between an annular piston operated by hydraulic pressure and a diaphragm spring.

従来、例えば、図７に示すように、油圧によって作動される環状ピストン２２０とダイヤフラムスプリング２４０との間に配設される油圧式クラッチレリーズ軸受装置においては、環状ピストン２２０に内径側が接続されるフランジ体２６０と、外径側にクラッチレリーズ軸受２３０の外輪２３１の外周面を覆う筒状体２５１とを有するカバー部材２５０を備えた構造のものがある。
また、カバー部材２５０のフランジ体２６０と筒状体２５１とは、一枚の鋼板がプレス加工（絞り加工）されることによって一体に形成される。
筒状体２５１の内部には、その内周面との間に環状の隙間をもってクラッチレリーズ軸受２３０の外輪２３１が組み込まれる。
さらに、筒状体２５１の開口縁に薄肉に加工された延出部分２５５ａが半径方向中心側へ曲げ加工されて環状部２５５が形成される。この際、クラッチレリーズ軸受２３０の外輪２３１の一端面がフランジ体２６０の内側面に当接した状態で、環状部２５５と、クラッチレリーズ軸受２３０の外輪２３１の他端面との間に調心用ばね２２５が介在される。
なお、油圧によって作動される環状ピストンとダイヤフラムスプリングとの間に配設される油圧式クラッチレリーズ軸受装置においては、例えば、特許文献１あるいは特許文献２に開示されている。
特開２００６−１８９０８６号公報 特開２００１−１３２７７３号公報 Conventionally, for example, as shown in FIG. 7, in a hydraulic clutch release bearing device disposed between an annular piston 220 and a diaphragm spring 240 that are actuated by hydraulic pressure, a flange whose inner diameter side is connected to the annular piston 220. There is a structure provided with a cover member 250 having a body 260 and a cylindrical body 251 that covers the outer peripheral surface of the outer ring 231 of the clutch release bearing 230 on the outer diameter side.
Further, the flange body 260 and the cylindrical body 251 of the cover member 250 are integrally formed by pressing (drawing) a single steel plate.
The outer ring 231 of the clutch release bearing 230 is incorporated in the cylindrical body 251 with an annular gap between the inner peripheral surface thereof.
Further, the extended portion 255a processed into a thin wall at the opening edge of the cylindrical body 251 is bent toward the center in the radial direction to form the annular portion 255. At this time, a centering spring is provided between the annular portion 255 and the other end surface of the outer ring 231 of the clutch release bearing 230 in a state where one end surface of the outer ring 231 of the clutch release bearing 230 is in contact with the inner side surface of the flange body 260. 225 is interposed.
A hydraulic clutch release bearing device disposed between an annular piston and a diaphragm spring operated by hydraulic pressure is disclosed in, for example, Patent Document 1 or Patent Document 2.
JP 2006-189086 A JP 2001-132773 A

ところで、図７に示すような油圧式クラッチレリーズ軸受装置においては、フランジ体２６０に所要とする剛性をもたせてフランジ体２６０の変形を防止する必要がある。このため、所要板厚（板厚が厚い）の一枚の鋼板がプレス加工（絞り加工）されることによってフランジ体２６０と筒状体２５１と一体に有するカバー部材２５０が形成される。そして、筒状体２５１の厚さ寸法は、フランジ体２６０の板厚寸法と略同等となる。
また、筒状体２５１の内径寸法は、クラッチレリーズ軸受２３０の外輪２３１の外周面との間に環状の隙間を形成できる大きさに設定する必要がある。
前記したようなことから、筒状体２５１の外径寸法が大きくなり、装置全体が大型化する。 Incidentally, in the hydraulic clutch release bearing device as shown in FIG. 7, it is necessary to give the flange body 260 the required rigidity to prevent the flange body 260 from being deformed. For this reason, the cover member 250 which has the flange body 260 and the cylindrical body 251 integrally is formed by press-working (drawing) one steel plate of required board thickness (thick board thickness). And the thickness dimension of the cylindrical body 251 becomes substantially equal to the plate thickness dimension of the flange body 260.
In addition, the inner diameter of the cylindrical body 251 needs to be set to a size that can form an annular gap with the outer peripheral surface of the outer ring 231 of the clutch release bearing 230.
As described above, the outer diameter of the cylindrical body 251 increases, and the entire apparatus increases in size.

この発明の目的は、前記問題点に鑑み、カバー部材の筒状体の外径寸法を小さくして装置全体の小型化を図ることができる油圧式クラッチレリーズ軸受装置を提供することである。   In view of the above problems, an object of the present invention is to provide a hydraulic clutch release bearing device in which the outer diameter of the cylindrical body of the cover member can be reduced to reduce the size of the entire device.

前記課題を解決するために、この発明の請求項１に係る油圧式クラッチレリーズ軸受装置は、油圧によって作動される環状ピストンとダイヤフラムスプリングとの間に配設されると共に、前記環状ピストンに内径側が接続されるフランジ体と、外径側にクラッチレリーズ軸受の外輪の外周面を覆う筒状体とを有するカバー部材を備えた油圧式クラッチレリーズ軸受装置であって、
前記カバー部材のフランジ体と筒状体とは別部品によって構成され、
前記筒状体は、前記フランジ体よりも薄肉の金属板によって円筒状に形成された筒胴部と、その筒胴部の一端縁から半径方向内方へ曲げ加工された環状の端壁部とを一体に有し、
前記筒状体の筒胴部内には、前記フランジ体と前記外輪とが順次に圧入されて固定されると共に、前記フランジ体の一側面が前記環状の端壁部に当接し、前記外輪の一端面が前記フランジ体の他側面に当接して前記筒状体と前記フランジ体と前記外輪とが一体化されていることを特徴とする。 In order to solve the above-described problems, a hydraulic clutch release bearing device according to a first aspect of the present invention is disposed between an annular piston and a diaphragm spring that are operated by hydraulic pressure, and an inner diameter side of the annular piston is disposed on the annular piston. A hydraulic clutch release bearing device having a cover member having a flange body to be connected and a cylindrical body covering an outer peripheral surface of an outer ring of the clutch release bearing on the outer diameter side,
The flange body and the cylindrical body of the cover member are constituted by separate parts,
The cylindrical body includes a cylindrical body portion formed in a cylindrical shape by a metal plate thinner than the flange body, and an annular end wall portion that is bent radially inward from one end edge of the cylindrical body portion. And have
The flange body and the outer ring are sequentially press-fitted and fixed in the cylindrical body portion of the cylindrical body, and one side surface of the flange body abuts on the annular end wall portion, An end surface contacts the other side surface of the flange body, and the cylindrical body, the flange body, and the outer ring are integrated.

前記構成によると、カバー部材のフランジ体と筒状体とを別部品によって構成し、フランジ体よりも薄肉の金属板よりなる筒状体の筒胴部内に、フランジ体とクラッチレリーズ軸受の外輪とを圧入固定して一体化することによって、カバー部材の筒状体の外径寸法を小さく抑えることができ、装置全体の小型化を良好に図ることができる。   According to the above configuration, the flange body and the cylindrical body of the cover member are configured as separate parts, and the flange body and the outer ring of the clutch release bearing are disposed in the cylindrical body portion of the cylindrical body made of a metal plate thinner than the flange body. By press-fitting and integrating, the outer diameter of the cylindrical member of the cover member can be kept small, and the overall size of the apparatus can be reduced favorably.

請求項２に係る油圧式クラッチレリーズ軸受装置は、請求項１に記載の油圧式クラッチレリーズ軸受装置であって、
筒状体の筒胴部は、その一端部にフランジ体の厚さ寸法に対応する筒長さをもって小径に絞られた小径の筒端部が形成されて段差筒状をなし、
前記小径の筒端部に前記フランジ体が圧入固定されていることを特徴とする。 A hydraulic clutch release bearing device according to claim 2 is the hydraulic clutch release bearing device according to claim 1,
The cylindrical body portion of the cylindrical body has a stepped cylindrical shape with a small-diameter cylindrical end portion that is narrowed to a small diameter with a cylindrical length corresponding to the thickness dimension of the flange body at one end thereof,
The flange body is press-fitted and fixed to an end portion of the small diameter cylinder.

前記構成によると、筒状体の筒胴部の一端部に形成された小径の筒端部にフランジ体を、筒状体の筒胴部にクラッチレリーズ軸受の外輪をそれぞれ所要とする締め代をもって良好に圧入固定することができる。
言い換えると、筒状体の筒胴部の一端部に小径の筒端部を形成することなく筒状体の筒胴部にフランジ体とクラッチレリーズ軸受の外輪とをそれぞれ圧入すると、フランジ体と外輪との外径寸法のバラツキ等によって一方の部材の締め代が不足し、空回りする恐れがあり、クラッチレリーズ軸受の軸受性能を悪化させることが想定される。
これに対し、前記したように筒状体の筒胴部の一端部に小径の筒端部を形成することによって、筒状体とフランジ体と外輪とを一体化して空回りを防止することができ、クラッチレリーズ軸受の軸受性能を維持することができる。 According to the above configuration, the flange body is provided at the end portion of the small diameter cylinder formed at one end of the cylindrical body portion of the cylindrical body, and the outer ring of the clutch release bearing is provided at the cylindrical body portion of the cylindrical body. It can be press-fitted and fixed well.
In other words, when the flange body and the outer ring of the clutch release bearing are respectively press-fitted into the cylindrical body portion of the cylindrical body without forming a small diameter cylindrical end portion at one end portion of the cylindrical body portion of the cylindrical body, the flange body and the outer ring It is assumed that the tightening allowance of one member is insufficient due to variations in the outer diameter of the member and the like, which may cause idling, and deteriorate the bearing performance of the clutch release bearing.
On the other hand, as described above, the cylindrical body, the flange body, and the outer ring can be integrated to prevent idle rotation by forming a small-diameter cylindrical end at one end of the cylindrical body of the cylindrical body. The bearing performance of the clutch release bearing can be maintained.

この発明を実施するための最良の形態について実施例にしたがって説明する。   The best mode for carrying out the present invention will be described in accordance with an embodiment.

〔実施例１〕
この発明の実施例１を図１〜図４にしたがって説明する。
図１はこの発明の実施例１に係る油圧式クラッチレリーズ軸受装置を示す縦断面図である。図２はクラッチレリーズ軸受のカバー部材を拡大して示す縦断面図である。図３はフランジ体の外径側フランジ部の面取り部を拡大して示す縦断面図である。図４はフランジ体が傾いた状態を示す説明図である。 [Example 1]
A first embodiment of the present invention will be described with reference to FIGS.
1 is a longitudinal sectional view showing a hydraulic clutch release bearing device according to Embodiment 1 of the present invention. FIG. 2 is an enlarged longitudinal sectional view showing a cover member of the clutch release bearing. FIG. 3 is an enlarged longitudinal sectional view showing a chamfered portion of the flange portion on the outer diameter side of the flange body. FIG. 4 is an explanatory view showing a state in which the flange body is inclined.

図１に示すように、クラッチ主軸１の外周面に組み付けられるシリンダ内筒体１０と、シリンダ外筒体１５との間には環状のシリンダ空間１６が形成され、このシリンダ空間１６には、シリンダ空間１６内に供給される油圧によって作動される環状ピストン２０が嵌挿されている。
シリンダ空間１６から突出される環状ピストン２０の突出部の先端側外周面には環状溝２１が凹設されている。 As shown in FIG. 1, an annular cylinder space 16 is formed between a cylinder inner cylinder 10 assembled on the outer peripheral surface of the clutch main shaft 1 and a cylinder outer cylinder 15. An annular piston 20 that is operated by hydraulic pressure supplied into the space 16 is fitted.
An annular groove 21 is recessed in the outer peripheral surface on the tip end side of the protruding portion of the annular piston 20 protruding from the cylinder space 16.

図１と図２に示すように、環状ピストン２０とダイヤフラムスプリング４０との間に配設される油圧式クラッチレリーズ軸受装置は、クラッチレリーズ軸受３０と、カバー部材５０とを備えている。
クラッチレリーズ軸受３０は、外輪３１と、この外輪３１の内周に同心状に配置される内輪３５と、外輪３１と内輪３５との間に保持器３３によって保持された状態で転動可能に配設される複数個の玉３２とを備えている。
また、内輪３５の一端部（ダイヤフラムスプリング４０に対向する側）にはダイヤフラムスプリング４０の内径側部分４１に接する押圧部３６が形成されている。 As shown in FIGS. 1 and 2, the hydraulic clutch release bearing device disposed between the annular piston 20 and the diaphragm spring 40 includes a clutch release bearing 30 and a cover member 50.
The clutch release bearing 30 is arranged to be able to roll while being held by a retainer 33 between an outer ring 31, an inner ring 35 concentrically disposed on the inner periphery of the outer ring 31, and the outer ring 31 and the inner ring 35. And a plurality of balls 32 to be provided.
In addition, a pressing portion 36 that is in contact with the inner diameter side portion 41 of the diaphragm spring 40 is formed at one end portion (side facing the diaphragm spring 40) of the inner ring 35.

図２に示すように、カバー部材５０は、環状ピストン２０に内径側が接続されるフランジ体６０と、外径側にクラッチレリーズ軸受３０の外輪３１の外周面を覆う筒状体５１とを有すると共に、これらフランジ体６０と筒状体５１とは別部品によって構成されている。
筒状体５１は、フランジ体６０よりも薄肉の金属板（鋼鉄板）のプレス加工（絞り加工）に形成され、外輪３１の外径寸法よりも僅かに小さい内径寸法の円筒状をなす筒胴部５２と、この筒胴部５２の一端部にフランジ体６０の厚さ寸法と略同じ筒長さをもって小径に絞られフランジ体６０の外径寸法（次に述べる外径側フランジ部６１の外径寸法）よりも僅かに小さい内径寸法をもつ小径の筒端部５３と、この小径の筒端部５３の端縁から半径方向内方へ曲げ加工された環状の端壁部５４とを一体に有して段差筒状をなしている。
そして、筒状体５１の小径の筒端部５３には、フランジ体６０が所定の締め代をもって圧入固定され、そのフランジ体６０の一側面が環状の端壁部５４の内面に当接する。
また、筒状体５１の筒胴部５２には、外輪３１が所定の締め代をもって圧入固定され、その外輪３１の一端面がフランジ体６０の他側面に当接した状態で、筒状体５１と、フランジ体６０と、外輪３１とが一体化されている。 As shown in FIG. 2, the cover member 50 includes a flange body 60 whose inner diameter side is connected to the annular piston 20, and a cylindrical body 51 that covers the outer peripheral surface of the outer ring 31 of the clutch release bearing 30 on the outer diameter side. The flange body 60 and the cylindrical body 51 are constituted by separate parts.
The cylindrical body 51 is formed by pressing (drawing) a metal plate (steel plate) that is thinner than the flange body 60, and forms a cylindrical body having an inner diameter that is slightly smaller than the outer diameter of the outer ring 31. The outer diameter of the flange body 60 and the outer diameter of the flange body 60 (to be described below) A small-diameter cylindrical end 53 having an inner diameter slightly smaller than the diameter (diameter) and an annular end wall 54 bent radially inward from the edge of the small-diameter cylindrical end 53 are integrated. It has a stepped cylindrical shape.
The flange body 60 is press-fitted and fixed to the small-diameter tube end 53 of the tubular body 51 with a predetermined allowance, and one side surface of the flange body 60 abuts against the inner surface of the annular end wall portion 54.
Further, the outer ring 31 is press-fitted and fixed to the cylinder body 52 of the cylindrical body 51 with a predetermined allowance, and the cylindrical body 51 is in a state where one end surface of the outer ring 31 is in contact with the other side surface of the flange body 60. And the flange body 60 and the outer ring | wheel 31 are integrated.

図２に示すように、フランジ体６０は、厚肉の金属板（鋼鉄板）のプレス加工に形成されると共に、外径側フランジ部６１と、第１屈曲部６２と、中間筒部６３と、第２屈曲部６４と、内径側フランジ部６５とを一体連続状に備えて縦断面Ｚ字状に形成されている。
外径側フランジ部６１は、その外径面が筒状体５１の小径の筒端部５３に所定の締め代で圧入固定され、この外径側フランジ部６１の内径端から第１屈曲部６２が所定の曲率半径でクラッチレリーズ軸受３０の内輪３５の内周面に向けて曲げられている。
中間筒部６３は、第１屈曲部６２の端縁からクラッチレリーズ軸受３０の内輪３５の内周面に沿って延びている。
中間筒部６３の端縁から第２屈曲部６４が所定の曲率半径で中心側に向けて曲げられ、この第２屈曲部６４の端縁から内径側フランジ部６５が環状ピストン２０の環状溝２１に向けて延出されている。そして、内径側フランジ部６５の内径端が環状溝２１の底面（外径面）と調心用の環状隙間を隔てて配置されると共に、環状溝２１の端壁面２３と内径側フランジ部６５との間には、皿ばね状の調心用ばね２５が配設され、この調心用ばね２５の弾発力によって内径側フランジ部６５の一側面が環状溝２１の押圧面２２に当接している。
すなわち、ダイヤフラムスプリング４０とクラッチレリーズ軸受３０との間に半径方向の偏心が生じたときには、ダイヤフラムスプリング４０に対し調心用ばね２５を介してクラッチレリーズ軸受３０が半径方向へ相対的に移動されることでダイヤフラムスプリング４０に対しクラッチレリーズ軸受３０が調心されるようになっている。 As shown in FIG. 2, the flange body 60 is formed by pressing a thick metal plate (steel plate), and has an outer diameter side flange portion 61, a first bent portion 62, an intermediate cylinder portion 63, and the like. The second bent portion 64 and the inner diameter side flange portion 65 are provided integrally and continuously, and are formed in a vertical Z-shape.
The outer diameter side flange portion 61 has an outer diameter surface that is press-fitted and fixed to the small-diameter tube end 53 of the cylindrical body 51 with a predetermined tightening allowance, and the first bent portion 62 extends from the inner diameter end of the outer diameter side flange portion 61. Is bent toward the inner peripheral surface of the inner ring 35 of the clutch release bearing 30 with a predetermined radius of curvature.
The intermediate cylinder portion 63 extends along the inner peripheral surface of the inner ring 35 of the clutch release bearing 30 from the edge of the first bent portion 62.
The second bent portion 64 is bent from the end edge of the intermediate cylindrical portion 63 toward the center side with a predetermined radius of curvature, and the inner diameter side flange portion 65 extends from the end edge of the second bent portion 64 to the annular groove 21 of the annular piston 20. It is extended toward the. The inner diameter end of the inner diameter side flange portion 65 is disposed with a bottom surface (outer diameter surface) of the annular groove 21 and an aligning annular gap, and the end wall surface 23 of the annular groove 21 and the inner diameter side flange portion 65 A disc spring-shaped aligning spring 25 is disposed between the inner flange side 65 and one side surface of the inner flange portion 65 abuts against the pressing surface 22 of the annular groove 21 due to the elastic force of the aligning spring 25. Yes.
That is, when a radial eccentricity occurs between the diaphragm spring 40 and the clutch release bearing 30, the clutch release bearing 30 is moved in the radial direction relative to the diaphragm spring 40 via the alignment spring 25. Thus, the clutch release bearing 30 is aligned with respect to the diaphragm spring 40.

また、この実施例１において、フランジ体６０の第１屈曲部６２や第２屈曲部６４に応力が集中することがないように、第１、第２の屈曲部６２、６４の曲率半径Ｒ１、Ｒ２が設定され、さらに、第１屈曲部６２の曲率半径Ｒ１は、第２屈曲部６４の曲率半径Ｒ２よりも大きく設定される。
例えば、第１屈曲部６２の曲率半径Ｒ１が２ｍｍ〜３ｍｍ程度に設定され、第２屈曲部６４の曲率半径Ｒ２が０．５ｍｍ〜２ｍｍ程度に設定される。 In the first embodiment, the curvature radii R1 of the first and second bent portions 62 and 64 are set so that stress does not concentrate on the first bent portion 62 and the second bent portion 64 of the flange body 60. R2 is set, and the radius of curvature R1 of the first bent portion 62 is set larger than the radius of curvature R2 of the second bent portion 64.
For example, the radius of curvature R1 of the first bent portion 62 is set to about 2 mm to 3 mm, and the radius of curvature R2 of the second bent portion 64 is set to about 0.5 mm to 2 mm.

また、この実施例１において、図３に示すように、フランジ体６０の外径側フランジ部６１の外径縁部には、所要とする面取り角度をもって面取り部６１ａが形成されている。
特に、この実施例１において、カバー部材５０の筒状体５１が外輪３１から抜け出る方向へ移動されることがないように、面取り部６１ａは、その内径端のエッジ部６１ｂの半径寸法をＡとし、クラッチレリーズ軸受３０の外輪３１端面の内径縁と外径側フランジ部６１との接触点Ｐの半径寸法をＢとしたときに、「Ａ≦Ｂ」の関係となるように設定されている。
なお、図１に示すように、フランジ体６０に沿って配設されたばね受け部材７０とシリンダ外筒体１５との間には、カバー部材５０と共にクラッチレリーズ軸受３０をダイヤフラムスプリング４０に向けて押圧する加圧ばね７５が配設されている。 Further, in the first embodiment, as shown in FIG. 3, a chamfered portion 61 a having a required chamfering angle is formed on the outer diameter edge portion of the outer diameter side flange portion 61 of the flange body 60.
In particular, in the first embodiment, the chamfered portion 61a has a radius dimension of the edge portion 61b at the inner diameter end thereof as A so that the cylindrical body 51 of the cover member 50 is not moved in the direction of coming out of the outer ring 31. When the radius dimension of the contact point P between the inner diameter edge of the outer ring 31 end face of the clutch release bearing 30 and the outer diameter side flange portion 61 is B, the relationship of “A ≦ B” is set.
In addition, as shown in FIG. 1, the clutch release bearing 30 is pressed toward the diaphragm spring 40 together with the cover member 50 between the spring receiving member 70 disposed along the flange body 60 and the cylinder outer cylinder body 15. A pressure spring 75 is disposed.

この実施例１に係る油圧式クラッチレリーズ軸受装置は上述したように構成される。
したがって、クラッチペダル（図示しない）の踏み込み動作に基づいてシリンダ空間１６内に油圧が供給されると、環状ピストン２０が押し出される。
すると、環状ピストン２０の環状溝２１一側内壁面の押圧面２２にカバー部材５０のフランジ体６０の内径側フランジ部６５が押圧されてカバー部材５０と共にクラッチレリーズ軸受３０が軸方向左側へ移動される。そして、クラッチレリーズ軸受３０の内輪３５端部の環状の押圧部３６によってダイヤフラムスプリング４０の内径側部分４１が押圧され、図示しないクラッチが作動（遮断）される。 The hydraulic clutch release bearing device according to the first embodiment is configured as described above.
Therefore, when the hydraulic pressure is supplied into the cylinder space 16 based on the depression of a clutch pedal (not shown), the annular piston 20 is pushed out.
Then, the inner diameter side flange portion 65 of the flange body 60 of the cover member 50 is pressed against the pressing surface 22 on the inner wall surface of the annular groove 21 of the annular piston 20, and the clutch release bearing 30 is moved to the left in the axial direction together with the cover member 50. The Then, the inner diameter side portion 41 of the diaphragm spring 40 is pressed by the annular pressing portion 36 at the end of the inner ring 35 of the clutch release bearing 30, and a clutch (not shown) is operated (disconnected).

さて、カバー部材５０を別部品よりなる筒状体５１とフランジ体６０によって構成し、フランジ体６０よりも薄肉の金属板よりなる筒状体５１の筒胴部５２内に、フランジ体６０とクラッチレリーズ軸受３０の外輪３１とを圧入固定して一体化することによって、カバー部材５０の筒状体５１の外径寸法を小さく抑えることができる。ひいては、油圧式クラッチレリーズ軸受装置全体の小型化を良好に図ることができる。   Now, the cover member 50 is constituted by a cylindrical body 51 and a flange body 60 made of different parts, and the flange body 60 and the clutch are placed in the cylindrical body portion 52 of the cylindrical body 51 made of a metal plate thinner than the flange body 60. By integrating the outer ring 31 of the release bearing 30 by press fitting, the outer diameter of the cylindrical body 51 of the cover member 50 can be kept small. As a result, it is possible to satisfactorily reduce the size of the entire hydraulic clutch release bearing device.

また、この実施例１において、筒状体５１の小径の筒端部５３にフランジ体６０を、筒胴部５２に外輪３１をそれぞれ所要とする締め代をもって不足なく良好に圧入固定することができる。このため、締め代の不足が原因となる筒状体５１に対するフランジ体６０あるいは外輪３１の相対的な空回りを防止することができ、クラッチレリーズ軸受３０の軸受性能を維持することができる。   Further, in the first embodiment, the flange body 60 and the outer ring 31 can be press-fitted and fixed satisfactorily with the required tightening margins at the small-diameter tube end 53 of the tubular body 51 and the outer ring 31 at the tubular body 52, respectively. . For this reason, relative idle rotation of the flange body 60 or the outer ring 31 with respect to the cylindrical body 51 due to insufficient tightening allowance can be prevented, and the bearing performance of the clutch release bearing 30 can be maintained.

また、この実施例１において、図２に示すように、フランジ体６０は、外径側フランジ部６１と、第１屈曲部６２と、中間筒部６３と、第２屈曲部６４と、内径側フランジ部６５とを一体連続状に備えて縦断面Ｚ字状に形成され、中間筒部６３は、第１屈曲部６２の端縁からクラッチレリーズ軸受３０の内輪３５の内周面に沿って延びている。このため、クラッチレリーズ軸受３０の内輪３５の内周側の空間を有効に利用してフランジ体６０の中間筒部６３を配置することができ、油圧式クラッチレリーズ軸受装置の小型化に効果が大きい。
また、フランジ体６０の板厚を積極的に厚くして剛性をより一層高めた場合においても、油圧式クラッチレリーズ軸受装置の大型化を抑制することが可能となる。
また、フランジ体６０の第１屈曲部６２や第２屈曲部６４に応力が集中することがないように、第１、第２の屈曲部６２、６４の曲率半径Ｒ１、Ｒ２が設定され、さらに、第１屈曲部６２の曲率半径Ｒ１は、第２屈曲部６４の曲率半径Ｒ２よりも大きく設定されるため、フランジ体６０の第１屈曲部６２や第２屈曲部６４に過大な応力が集中して損傷されることを防止することができ、耐久性の向上を図ることができる。 In Example 1, as shown in FIG. 2, the flange body 60 includes an outer diameter side flange portion 61, a first bent portion 62, an intermediate cylindrical portion 63, a second bent portion 64, and an inner diameter side. The flange portion 65 is integrally and continuously formed, and is formed in a Z-shaped longitudinal section. The intermediate cylinder portion 63 extends from the end edge of the first bent portion 62 along the inner peripheral surface of the inner ring 35 of the clutch release bearing 30. ing. For this reason, the intermediate cylinder part 63 of the flange body 60 can be disposed by effectively utilizing the space on the inner peripheral side of the inner ring 35 of the clutch release bearing 30, which is highly effective in reducing the size of the hydraulic clutch release bearing device. .
Moreover, even when the plate thickness of the flange body 60 is positively increased to further increase the rigidity, it is possible to suppress an increase in size of the hydraulic clutch release bearing device.
Further, the radii of curvature R1 and R2 of the first and second bent portions 62 and 64 are set so that stress does not concentrate on the first bent portion 62 and the second bent portion 64 of the flange body 60, and Since the radius of curvature R1 of the first bent portion 62 is set larger than the radius of curvature R2 of the second bent portion 64, excessive stress is concentrated on the first bent portion 62 and the second bent portion 64 of the flange body 60. Damage can be prevented, and durability can be improved.

また、この実施例１において、図３に示すように、フランジ体６０の外径側フランジ部６１の面取り部６１ａは、その内径端のエッジ部６１ｂの半径寸法をＡとし、クラッチレリーズ軸受３０の外輪３１端面の内径縁と外径側フランジ部６１との接触点Ｐの半径寸法をＢとしたときに、「Ａ≦Ｂ」の関係となるように設定されている。
これによって、図４に示すように、フランジ体６０の外径側フランジ部６１が接触点Ｂを支点として図４に向かって時計回り方向へ傾いた場合、外径側フランジ部６１の面取り部６１ａ内径端のエッジ部６１ｂが外輪３１端面側へ変位する。このため、カバー部材５０の筒状体５１が外輪３１から不測に抜け出る方向へ移動されることを防止することができる。
また、図５に示すように、フランジ体６０の外径側フランジ部６１の外径縁部に所要とする曲率半径を面取り部６１ａ’を形成しても同等の作用効果を奏する。 Further, in the first embodiment, as shown in FIG. 3, the chamfered portion 61 a of the outer diameter side flange portion 61 of the flange body 60 has a radius dimension of the edge portion 61 b at the inner diameter end of the clutch release bearing 30. When the radius dimension of the contact point P between the inner diameter edge of the end face of the outer ring 31 and the outer diameter side flange portion 61 is B, the relation of “A ≦ B” is set.
As a result, as shown in FIG. 4, when the outer diameter side flange portion 61 of the flange body 60 is tilted clockwise with respect to the contact point B toward FIG. 4, the chamfered portion 61 a of the outer diameter side flange portion 61. The edge portion 61b at the inner diameter end is displaced toward the outer ring 31 end face side. For this reason, it can prevent that the cylindrical body 51 of the cover member 50 is moved to the direction which pulls out from the outer ring | wheel 31 unexpectedly.
Further, as shown in FIG. 5, even if the chamfered portion 61a ′ is formed to have a required radius of curvature at the outer diameter edge portion of the outer diameter side flange portion 61 of the flange body 60, the same effect can be obtained.

なお、この発明は前記実施例１に限定するものではなく、この発明の要旨を逸脱しない範囲内において、種々なる形態で実施することもできる。
例えば、前記実施例１においては、カバー部材５０の筒状体５１の端部に小径の筒端部５３を形成したが、小径の筒端部５３は必ずしも設けなくてもこの発明を実施することができる。
すなわち、図６に示すように、カバー部材１５０の筒状体１５１を、フランジ体１６０よりも薄肉の金属板（鋼鉄板）によって円筒状に形成された筒胴部１５２と、その筒胴部１５２の一端縁から半径方向内方へ曲げ加工された環状の端壁部１５４とによって一体に形成し、筒胴部１５２内に、フランジ体１６０とクラッチレリーズ軸受３０の外輪３１とを順次に圧入固定してもこの発明を実施することができる。
また、図６に示すように、筒胴部１５２内にフランジ体１６０とクラッチレリーズ軸受３０の外輪３１とを順次に圧入固定した後、筒状体（筒胴部１５２）１５１の他端縁１５２ａを半径方向内方へ環状に折り曲げて環状部１５５を形成することによって、筒状体１５１と、フランジ体１６０と外輪３１とを強固に結合することが望ましい。 In addition, this invention is not limited to the said Example 1, In the range which does not deviate from the summary of this invention, it can also be implemented with a various form.
For example, in the first embodiment, the small-diameter tube end 53 is formed at the end of the cylindrical body 51 of the cover member 50. However, the present invention may be implemented even if the small-diameter tube end 53 is not necessarily provided. Can do.
That is, as shown in FIG. 6, the cylindrical body 151 of the cover member 150 is formed into a cylindrical shape by a metal plate (steel plate) thinner than the flange body 160, and the cylindrical body portion 152. Are integrally formed by an annular end wall portion 154 bent radially inward from one end edge of the flange body 160, and the flange body 160 and the outer ring 31 of the clutch release bearing 30 are sequentially press-fitted and fixed in the cylindrical body portion 152. Even so, the present invention can be implemented.
Further, as shown in FIG. 6, after the flange body 160 and the outer ring 31 of the clutch release bearing 30 are sequentially press-fitted and fixed in the cylindrical body 152, the other end edge 152a of the cylindrical body (cylinder body 152) 151 is obtained. It is desirable that the tubular body 151, the flange body 160, and the outer ring 31 be firmly coupled to each other by bending the ring shape radially inwardly to form the annular portion 155.

この発明の実施例１に係る油圧式クラッチレリーズ軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the hydraulic clutch release bearing apparatus which concerns on Example 1 of this invention. 同じくクラッチレリーズ軸受のカバー部材を拡大して示す縦断面図である。It is the longitudinal cross-sectional view which expands and similarly shows the cover member of a clutch release bearing. 同じくカバー部材のフランジ体の外径側フランジ部の面取り部を拡大して示す縦断面図である。It is a longitudinal cross-sectional view which expands and shows the chamfering part of the outer diameter side flange part of the flange body of a cover member similarly. 同じくフランジ体が傾いた状態を示す説明図である。It is explanatory drawing which shows the state which the flange body inclined similarly. カバー部材のフランジ体の外径側フランジ部の面取り部がアール面に形成された実施態様を示す縦断面図である。It is a longitudinal cross-sectional view which shows the embodiment by which the chamfered part of the outer diameter side flange part of the flange body of a cover member was formed in the rounded surface. カバー部材の筒状体（筒胴部）が全長にわたって同径に形成された実施態様を示す縦断面図である。It is a longitudinal cross-sectional view which shows the embodiment by which the cylindrical body (cylinder trunk | drum) of the cover member was formed in the same diameter over the full length. 従来の油圧式クラッチレリーズ軸受装置のスリーブの軸線が傾いた状態でレリーズフォークによって軸方向へ摺動される状態を示す説明図である。It is explanatory drawing which shows the state slid to an axial direction with a release fork in the state in which the axis line of the sleeve of the conventional hydraulic clutch release bearing apparatus inclined.

符号の説明Explanation of symbols

１０ シリンダ内筒体
１５ シリンダ外筒体
１６ シリンダ空間
２０ 環状ピストン
３０ クラッチレリーズ軸受
３１ 外輪
３５ 内輪
４０ ダイヤフラムスプリング
５０ カバー部材
５１ 筒状体
５２ 筒胴部
５３ 小径の筒端部
５４ 環状の端壁部
６０ フランジ体 DESCRIPTION OF SYMBOLS 10 Cylinder inner cylinder 15 Cylinder outer cylinder 16 Cylinder space 20 Annular piston 30 Clutch release bearing 31 Outer ring 35 Inner ring 40 Diaphragm spring 50 Cover member 51 Cylindrical body 52 Cylindrical barrel part 53 Small-diameter cylindrical end part 54 Annular end wall part 60 Flange body

Claims (2)

油圧によって作動される環状ピストンとダイヤフラムスプリングとの間に配設されると共に、前記環状ピストンに内径側が接続されるフランジ体と、外径側にクラッチレリーズ軸受の外輪の外周面を覆う筒状体とを有するカバー部材を備えた油圧式クラッチレリーズ軸受装置であって、
前記カバー部材のフランジ体と筒状体とは別部品によって構成され、
前記筒状体は、前記フランジ体よりも薄肉の金属板によって円筒状に形成された筒胴部と、その筒胴部の一端縁から半径方向内方へ曲げ加工された環状の端壁部とを一体に有し、
前記筒状体の筒胴部内には、前記フランジ体と前記外輪とが順次に圧入されて固定されると共に、前記フランジ体の一側面が前記環状の端壁部に当接し、前記外輪の一端面が前記フランジ体の他側面に当接して前記筒状体と前記フランジ体と前記外輪とが一体化されていることを特徴とする油圧式クラッチレリーズ軸受装置。 A flange that is disposed between an annular piston that is actuated by hydraulic pressure and a diaphragm spring, and that has an inner diameter side connected to the annular piston, and a cylindrical body that covers the outer peripheral surface of the outer ring of the clutch release bearing on the outer diameter side A hydraulic clutch release bearing device comprising a cover member having
The flange body and the cylindrical body of the cover member are constituted by separate parts,
The cylindrical body includes a cylindrical body portion formed in a cylindrical shape by a metal plate thinner than the flange body, and an annular end wall portion that is bent radially inward from one end edge of the cylindrical body portion. And have
The flange body and the outer ring are sequentially press-fitted and fixed in the cylindrical body portion of the cylindrical body, and one side surface of the flange body abuts on the annular end wall portion, A hydraulic clutch release bearing device characterized in that an end surface abuts against the other side surface of the flange body, and the cylindrical body, the flange body, and the outer ring are integrated. 請求項１に記載の油圧式クラッチレリーズ軸受装置であって、
筒状体の筒胴部は、その一端部にフランジ体の厚さ寸法に対応する筒長さをもって小径に絞られた小径の筒端部が形成されて段差筒状をなし、
前記小径の筒端部に前記フランジ体が圧入固定されていることを特徴とする油圧式クラッチレリーズ軸受装置。 The hydraulic clutch release bearing device according to claim 1,
The cylindrical body portion of the cylindrical body has a stepped cylindrical shape with a small-diameter cylindrical end portion that is narrowed to a small diameter with a cylindrical length corresponding to the thickness dimension of the flange body at one end thereof,
The hydraulic clutch release bearing device, wherein the flange body is press-fitted and fixed to an end portion of the small diameter cylinder.
JP2008007928A 2008-01-17 2008-01-17 Hydraulic clutch release bearing device Expired - Fee Related JP5018498B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108869533A (en) * 2018-08-15 2018-11-23 江苏联动轴承股份有限公司 A kind of elastic slice bearing
CN110173509A (en) * 2018-02-21 2019-08-27 Ntn-Snr轴承股份有限公司 Equipped with the automobile clutch release bearing of sealing device on rear side of raceway

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57177426A (en) * 1981-04-06 1982-11-01 Esukeiefu Yuu Kei Ltd Self-aligning clutch releasing device
JP2002364671A (en) * 2001-06-11 2002-12-18 Koyo Seiko Co Ltd Aligning spring for clutch release bearing

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57177426A (en) * 1981-04-06 1982-11-01 Esukeiefu Yuu Kei Ltd Self-aligning clutch releasing device
JP2002364671A (en) * 2001-06-11 2002-12-18 Koyo Seiko Co Ltd Aligning spring for clutch release bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110173509A (en) * 2018-02-21 2019-08-27 Ntn-Snr轴承股份有限公司 Equipped with the automobile clutch release bearing of sealing device on rear side of raceway
CN108869533A (en) * 2018-08-15 2018-11-23 江苏联动轴承股份有限公司 A kind of elastic slice bearing

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