JP2009144895A - Clutch release bearing - Google Patents

Clutch release bearing Download PDF

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Publication number
JP2009144895A
JP2009144895A JP2007325814A JP2007325814A JP2009144895A JP 2009144895 A JP2009144895 A JP 2009144895A JP 2007325814 A JP2007325814 A JP 2007325814A JP 2007325814 A JP2007325814 A JP 2007325814A JP 2009144895 A JP2009144895 A JP 2009144895A
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JP
Japan
Prior art keywords
seal
clutch release
release bearing
seal member
outer diameter
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Withdrawn
Application number
JP2007325814A
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Japanese (ja)
Inventor
Katsuaki Sasaki
克明 佐々木
Yasuyuki Katayama
康行 片山
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2007325814A priority Critical patent/JP2009144895A/en
Publication of JP2009144895A publication Critical patent/JP2009144895A/en
Withdrawn legal-status Critical Current

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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
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • 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
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/083—Actuators therefor

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch release bearing achieving improved sealability, especially improved mud water resistance without increasing a bearing torque. <P>SOLUTION: This clutch release bearing 10 includes: an outer ring 12 forming a rotation side and made to serve as an outer member abutting on the rotary member of a clutch device; an inner ring 11 forming a stationary side and made to serve as an inner member arranged on the inner periphery of the outer ring 12; and a first seal member 15 having an outside diameter end portion fixed to the inside diameter surface of the outer ring 12 and an inside diameter end portion brought into contact with the outside diameter surface of the inner ring 11, and sealing at one end on a rear side an annular space formed between the outer ring 12 and the inner ring 11. The inner ring 11 is provided with a second flange portion 11b extending to an outside diameter side, and an axial seal clearance S2, that is, a non-contact seal, is formed between the second flange portion 11b and the first seal member 15. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は自動車をはじめとする車両のクラッチ装置に組み込まれるクラッチレリーズ軸受に関する。   The present invention relates to a clutch release bearing incorporated in a clutch device of a vehicle including an automobile.

クラッチレリーズ軸受装置は、マニュアルトランスミッション車のエンジンとトランスミッションとの間に配設され、クラッチペダルの操作に伴って軸方向移動し、クラッチのＯＮ／ＯＦＦを切り替えるものである。クラッチレリーズ軸受装置に組み込まれるクラッチレリーズ軸受として、例えば特許文献１に記載のように、クラッチ装置の回転部材との当接部を有する回転側の外側部材（外輪）と、外輪の内周に配設された静止側の内側部材（内輪）と、両輪間に介在する複数の転動体（ボール）とを備えるものが公知である。   The clutch release bearing device is disposed between an engine and a transmission of a manual transmission vehicle, and moves in the axial direction in accordance with the operation of a clutch pedal to switch on / off of the clutch. As a clutch release bearing incorporated in a clutch release bearing device, for example, as disclosed in Patent Document 1, a rotating side outer member (outer ring) having a contact portion with a rotating member of the clutch device and an inner periphery of the outer ring are arranged. It is known that includes a stationary-side inner member (inner ring) provided and a plurality of rolling elements (balls) interposed between the two wheels.

この種のクラッチレリーズ軸受には、軸受内部に充填したグリース等の潤滑材の外部漏洩、および軸受内部への泥水等の異物侵入を防止する目的で、外輪と内輪の間を密封するシール部材が設けられる。上記特許文献１中に記載のシール部材は、外径端部を外輪の内径面に固定すると共に、内径端部を所定の半径方向隙間を介して内輪の外径面と対向させた、いわゆる非接触型であり、安定したシール性能を長期に亘って維持可能であることから広く用いられている。
特開平０７−７１４８２号公報 This type of clutch release bearing has a sealing member that seals between the outer ring and the inner ring in order to prevent external leakage of lubricant such as grease filled in the bearing and entry of foreign matter such as muddy water into the bearing. Provided. The sealing member described in Patent Document 1 fixes the outer diameter end portion to the inner diameter surface of the outer ring, and is a so-called non-contact type in which the inner diameter end portion is opposed to the outer diameter surface of the inner ring via a predetermined radial clearance. It is a contact type and is widely used because it can maintain stable sealing performance over a long period of time.
JP 07-71482 A

ところで、近年では、シール性能の向上を目的として、内径端部に設けたゴム製のリップを内輪の外径面に接触させた、いわゆる接触型のシール部材を用いる場合がある。さらに、近年では、クラッチレリーズ軸受装置が泥水に浸るような過酷な使用環境下においても、軸受内部に泥水が浸入することのない高いシール性能を要求される場合がある。かかるシール性能向上（特に、耐泥水性の向上）の要請に対応するための手段として、内輪の外径面に接触させるリップの数を増加させる、リップの接触代を増大させる等の手段を採用することが考えられるが、このような手段を採用すると、軸受トルクの増大、ひいてはクラッチ装置の機能低下を招く。   By the way, in recent years, for the purpose of improving the sealing performance, a so-called contact-type sealing member in which a rubber lip provided at the inner diameter end portion is brought into contact with the outer diameter surface of the inner ring may be used. Furthermore, in recent years, there is a case where high sealing performance is required in which the muddy water does not enter the bearing even under a severe use environment where the clutch release bearing device is immersed in the muddy water. As measures to meet the demand for such improved sealing performance (especially improved muddy water resistance), measures such as increasing the number of lips in contact with the outer diameter surface of the inner ring and increasing the contact allowance of the lip are adopted. However, if such a means is adopted, an increase in bearing torque and a decrease in the function of the clutch device are caused.

本発明の課題は、軸受トルクを増大させることなく、シール性能、特に耐泥水性の向上を図ったクラッチレリーズ軸受を提供することにある。   An object of the present invention is to provide a clutch release bearing that improves sealing performance, particularly, muddy water resistance without increasing bearing torque.

上記課題を解決するため、本発明では、クラッチ装置の回転部材との当接部を有する回転側の外側部材と、外側部材の内周に配設された静止側の内側部材と、外側部材と内側部材の間に介在する複数の転動体と、外径端部が外側部材の内径面に固定されると共に、内径端部が内側部材の外径面に接触して、外側部材と内側部材の間を密封するシール部材とを備えるクラッチレリーズ軸受において、内側部材に外径側に延在する鍔部を設け、該鍔部とシール部材との間に軸方向のシール隙間を形成したことを特徴とするクラッチレリーズ軸受を提供する。   In order to solve the above problems, in the present invention, a rotating side outer member having a contact portion with a rotating member of a clutch device, a stationary side inner member disposed on the inner periphery of the outer member, and an outer member, The plurality of rolling elements interposed between the inner members and the outer diameter end are fixed to the inner diameter surface of the outer member, and the inner diameter end contacts the outer diameter surface of the inner member, In a clutch release bearing comprising a seal member that seals between, a flange portion extending to the outer diameter side is provided on the inner member, and an axial seal gap is formed between the flange portion and the seal member. A clutch release bearing is provided.

上記のように、本発明に係るクラッチレリーズ軸受は、内側部材に外径側に延在する鍔部を設け、該鍔部とシール部材との間に軸方向のシール隙間を形成したことを特徴とするものである。かかる構成では、シール部材の内径端部と内側部材の外径面とで形成される接触シールよりも軸受外方側に非接触シールが追加され、外側部材の回転時には、外側部材の回転力（回転に伴って生じる遠心力）によって異物（特に泥水）の侵入を防止することが可能となる。仮に、このシール隙間を越えて泥水が浸入したとしても、この泥水はシール部材の内径端部と内側部材の外径面との接触部（接触シール）で捕捉することができる。また、前述のとおり、本発明で付加されるシール機能は、いわゆる非接触シールである。以上のことから、本発明によれば、軸受トルクを増大させることなく、シール性能の向上を図ることができる。   As described above, the clutch release bearing according to the present invention is characterized in that the inner member is provided with the flange portion extending to the outer diameter side, and an axial seal gap is formed between the flange portion and the seal member. It is what. In such a configuration, a non-contact seal is added to the bearing outer side than the contact seal formed by the inner diameter end portion of the seal member and the outer diameter surface of the inner member, and when the outer member rotates, the rotational force ( Intrusion of foreign matter (especially muddy water) can be prevented by the centrifugal force generated with rotation. Even if the muddy water enters through the seal gap, the muddy water can be captured at the contact portion (contact seal) between the inner diameter end of the seal member and the outer diameter surface of the inner member. As described above, the sealing function added in the present invention is a so-called non-contact seal. From the above, according to the present invention, it is possible to improve the sealing performance without increasing the bearing torque.

軸方向のシール隙間の隙間幅ｔは、０ｍｍ＜ｔ≦０．８ｍｍとするのが望ましい。まず、隙間幅ｔを０ｍｍよりも大きくするのは、内側部材の鍔部とシール部材との間に形成するシールを非接触シールとするための必須条件である。また、隙間幅ｔを０．８ｍｍ以下とするのは、本願発明者らが鋭意研究を重ねた結果、跳ね掛けられる泥水の粒子（水滴）の直径は、その大半が０．８ｍｍよりも大径であり、この隙間幅を境界として、シール性能が大きく異なることを見出したためである。   The gap width t of the axial seal gap is preferably 0 mm <t ≦ 0.8 mm. First, increasing the gap width t to be greater than 0 mm is an essential condition for making the seal formed between the flange of the inner member and the seal member a non-contact seal. In addition, the gap width t is set to 0.8 mm or less, as a result of the present inventors' extensive research, the diameter of muddy water particles (water droplets) splashed is mostly larger than 0.8 mm. This is because it has been found that the sealing performance differs greatly with this gap width as a boundary.

軸方向のシール隙間は、シール部材にゴム製の突出部を設け、該突出部の一端面と鍔部の対向面との間に形成することができる。ゴム製の突出部は型成形することができるため、金属材料で形成される場合が多い内側部材に比べて形状自由度が高く、上記のようなシール隙間を容易かつ高精度に形成することができる。   The seal gap in the axial direction can be formed between the one end surface of the protrusion and the opposing surface of the flange portion by providing a rubber protrusion on the seal member. Since the rubber protrusions can be molded, the degree of freedom in shape is higher than that of the inner member, which is often formed of a metal material, and the above-described seal gap can be easily and highly accurately formed. it can.

突出部は、シール部材の円周方向全周に亘って設けることができる他、半径方向に対して傾斜した羽根形状とし、かつシール部材の円周方向で断続的に複数設けることもできる。後者の形態とした場合、外側部材の回転時に送風作用を生じさせることができ、泥水の浸入量を効果的に減少させることができる。   In addition to being provided over the entire circumference in the circumferential direction of the seal member, the projecting portion may have a blade shape inclined with respect to the radial direction and may be provided intermittently in the circumferential direction of the seal member. When it is set as the latter form, it can produce a ventilation effect at the time of rotation of an outer member, and can reduce the intrusion amount of muddy water effectively.

なお、ゴム製の突出部を形成するゴム材料としては、少なくとも耐水性を有し、さらには耐摩耗性を具備するものが望ましく、例えば、ニトリルゴム（ＮＢＲ）、水素添加ニトリルゴム（Ｈ−ＮＢＲ）、耐熱ニトリルゴム、フッ素ゴム（ＦＫＭ）等が好適に使用可能である。   In addition, as a rubber material which forms the protrusion part made from rubber | gum, what has water resistance at least, and also has abrasion resistance is desirable, for example, nitrile rubber (NBR), hydrogenated nitrile rubber (H-NBR) ), Heat-resistant nitrile rubber, fluorine rubber (FKM) and the like can be suitably used.

シール部材は、芯金およびこれを被覆するゴム製の被覆層からなるものとすることができ、この場合、被覆層の一部に前記突出部を形成することができる。この場合、当該シール部材の外側部材の内径面への組み込みを考慮すると、突出部の外径側に、シール部材組み込み用の押圧面を設けるのが望ましい。ここで言う押圧面の形成態様の具体例として、軸線と直交する方向の平坦面を挙げることができる。   The seal member can be composed of a cored bar and a rubber coating layer covering the cored bar, and in this case, the protruding portion can be formed on a part of the coating layer. In this case, considering the incorporation of the seal member into the inner diameter surface of the outer member, it is desirable to provide a pressing surface for incorporating the seal member on the outer diameter side of the protrusion. As a specific example of the pressing surface formation described here, a flat surface in a direction orthogonal to the axis can be exemplified.

以上に示すクラッチレリーズ軸受は、例えば油圧によって駆動されるダイレクトシリンダタイプのクラッチレリーズ軸受装置に組み込んで好適に使用可能である。   The clutch release bearing described above can be suitably used by being incorporated in, for example, a direct cylinder type clutch release bearing device driven by hydraulic pressure.

以上のように、本発明によれば、軸受トルクを増大させることなく、シール性能の向上、特に耐泥水性の向上を図ったクラッチレリーズ軸受を提供することができる。   As described above, according to the present invention, it is possible to provide a clutch release bearing that is improved in sealing performance, particularly in muddy water resistance without increasing bearing torque.

以下、本発明の実施形態を図面に基づいて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１は本発明に係るクラッチレリーズ軸受を組み込んだクラッチレリーズ軸受装置、詳細には、油圧によって駆動されるダイレクトシリンダタイプのクラッチレリーズ軸受装置を概念的に示す断面図である。同図に示すクラッチレリーズ軸受装置１は、ギアボックスのケーシング５０に取り付けられた固定体３０と、固定体３０に対して軸方向移動可能に設けられ、固定体３０と協働して容積可変チャンバ４０を形成する可動体２０とで主要部が構成される。容積可変チャンバ４０には図示しない制御用油圧発生器が接続され、チャンバ４０内には制御流体としてのオイルが充満されている。なお、この図１は、クラッチが係合している状態を示すものである。また、以下の説明では、便宜上、図中左側をフロント側、図中右側をリア側という。   FIG. 1 is a sectional view conceptually showing a clutch release bearing device incorporating a clutch release bearing according to the present invention, and more specifically, a direct cylinder type clutch release bearing device driven by hydraulic pressure. A clutch release bearing device 1 shown in FIG. 1 is provided with a fixed body 30 attached to a casing 50 of a gear box, and is provided so as to be movable in the axial direction with respect to the fixed body 30. The main part is composed of the movable body 20 forming 40. A control hydraulic pressure generator (not shown) is connected to the variable volume chamber 40, and the chamber 40 is filled with oil as a control fluid. FIG. 1 shows a state where the clutch is engaged. In the following description, for the sake of convenience, the left side in the figure is referred to as the front side and the right side in the figure is referred to as the rear side.

固定体３０は、リア側一端に容積可変チャンバ４０の底部を構成するラジアルエッジ３４が設けられたガイドチューブ３３と、内径面に設けた溝部３２にラジアルエッジ３４の外径側一端が嵌合された円筒状の外側本体３１とで主要部が構成される。   The fixed body 30 has a guide tube 33 provided with a radial edge 34 constituting the bottom of the variable volume chamber 40 at one end on the rear side, and an outer diameter side end of the radial edge 34 fitted in a groove 32 provided on the inner diameter surface. The cylindrical outer body 31 constitutes a main part.

可動体２０は、ピストン支持チューブ２１を介してガイドチューブ３３に外嵌されたピストン２２と、ピストン２２のフロント側一端に配設され、図示しないクラッチ装置の回転部材（ダイヤフラムスプリング）との当接部を有するクラッチレリーズ軸受１０とを主要な構成部材として備える。ピストン２２は、軸方向に延在する外側円筒部２２ａおよび内側円筒部２２ｂと、両円筒部をフロント側一端で接続する環状部２２ｃと、外側円筒部２２ａの基端部から外径側に延在するフランジ部２２ｄとを有する。ピストン２２のうち、内側円筒部２２ｂは外側本体３１の内周に挿入され、固定体３０との間に容積可変チャンバ４０を形成し、フランジ部２２ｄは、外側円筒部２２ａ（ピストン２２）の外周に配設された予圧スプリング２４のフロント側一端を係止する役割を担う。ピストン支持チューブ２１のフロント側一端はピストン２２の環状部２２ｃを若干越えて延設され、この延設された部分の外径面に形成された環状溝２１ａに皿ばね２３が嵌合される。皿ばね２３は、ピストン２２の環状部２２ｃと協働してクラッチレリーズ軸受１０（の内輪１１）を弾性的に支持するためのばね力を有するものであり、クラッチレリーズ軸受１０は、皿ばね２３のばね力でピストン２２側に押圧されることによって調心が許容されるようになっている。   The movable body 20 is disposed on the front end of the piston 22 that is externally fitted to the guide tube 33 via the piston support tube 21 and is in contact with a rotating member (diaphragm spring) of a clutch device (not shown). A clutch release bearing 10 having a portion is provided as a main constituent member. The piston 22 includes an outer cylindrical portion 22a and an inner cylindrical portion 22b that extend in the axial direction, an annular portion 22c that connects the two cylindrical portions at one end on the front side, and an outer diameter extending from the base end portion of the outer cylindrical portion 22a. And an existing flange portion 22d. Among the pistons 22, the inner cylindrical portion 22 b is inserted into the inner periphery of the outer body 31 to form a variable volume chamber 40 with the fixed body 30, and the flange portion 22 d is an outer periphery of the outer cylindrical portion 22 a (piston 22). It plays the role which latches the front side one end of the preload spring 24 arrange | positioned by this. One end on the front side of the piston support tube 21 extends slightly beyond the annular portion 22c of the piston 22, and a disc spring 23 is fitted into an annular groove 21a formed on the outer diameter surface of the extended portion. The disc spring 23 has a spring force for elastically supporting the clutch release bearing 10 (the inner ring 11 thereof) in cooperation with the annular portion 22 c of the piston 22. The clutch release bearing 10 is a disc spring 23. Alignment is allowed by being pressed toward the piston 22 by the spring force.

以上の構成からなるクラッチレリーズ軸受装置１において、クラッチを解除状態にする際の各部材の挙動を簡単に説明する。まず、図示しない油圧発生器によって容積可変チャンバ４０内のオイルが加圧されると、容積可変チャンバ４０の容積が増大するよう、ピストン２２がフロント側に移動する。ピストン２２は移動中にクラッチレリーズ軸受１０を作動させる。クラッチレリーズ軸受１０が作動すると、図示しないダイヤフラムスプリングにはスラスト力が付加され、これによりクラッチが解除される。   In the clutch release bearing device 1 configured as described above, the behavior of each member when the clutch is released will be briefly described. First, when oil in the variable volume chamber 40 is pressurized by a hydraulic pressure generator (not shown), the piston 22 moves to the front side so that the volume of the variable volume chamber 40 increases. The piston 22 operates the clutch release bearing 10 during movement. When the clutch release bearing 10 is actuated, a thrust force is applied to a diaphragm spring (not shown), thereby releasing the clutch.

以下、クラッチレリーズ軸受１０について詳述する。図示例のクラッチレリーズ軸受１０は、いわゆるアンギュラ玉軸受からなり、図２にも拡大して示すように、複数のボール１３を介して相対回転可能に設けられた内側部材としての内輪１１および外側部材としての外輪１２と、両輪間に組み込まれ、ボール１３を円周方向等間隔で保持する保持器１４と、両輪間に形成される環状空間の両端開口部に配設された第１および第２シール部材１５，１６とを備え、両輪間に形成される環状空間には潤滑材としてのグリースが充満される。このクラッチレリーズ軸受１０は、内輪１１が静止側、外輪１２が回転側を構成する外輪回転タイプの軸受である。   Hereinafter, the clutch release bearing 10 will be described in detail. The clutch release bearing 10 of the illustrated example is a so-called angular ball bearing, and as shown in an enlarged manner in FIG. 2, an inner ring 11 and an outer member as inner members provided so as to be relatively rotatable via a plurality of balls 13. As an outer ring 12, a retainer 14 that is incorporated between the two wheels and holds the balls 13 at equal intervals in the circumferential direction, and first and second openings disposed at both ends of an annular space formed between the two wheels. Sealing members 15 and 16 are provided, and an annular space formed between both wheels is filled with grease as a lubricant. The clutch release bearing 10 is an outer ring rotating type bearing in which an inner ring 11 is a stationary side and an outer ring 12 is a rotating side.

内輪１１は、例えば鋼板のプレス成形品とされ、フロント側一端から内径側に延び、図１に示すように、先端部がピストン２２の環状部２２ｃと皿ばね２３との間に介在する第１鍔部１１ａと、リア側一端から外径側に延び、外輪１２のリア側一端よりも軸受外方側に位置する第２鍔部１１ｂとを有する。第１鍔部１１ａのリア側端面は、これが接するピストン２２の環状部２２ｃの端面形状に対応するかたちで平坦面に形成される。   The inner ring 11 is, for example, a press-formed product of a steel plate, extends from the front side end to the inner diameter side, and has a first end interposed between the annular portion 22c of the piston 22 and the disc spring 23 as shown in FIG. The flange portion 11a has a second flange portion 11b that extends from the rear end to the outer diameter side and is positioned on the bearing outer side from the rear end of the outer ring 12. The rear side end surface of the first flange portion 11a is formed into a flat surface in a form corresponding to the end surface shape of the annular portion 22c of the piston 22 with which the first flange portion 11a contacts.

外輪１２は、内輪１１同様に鋼板のプレス成形品とされ、内径側に延在し、図示しないダイヤフラムスプリングに当接する鍔部１２ａを有する。外輪１２の鍔部１２ａは、ダイヤフラムスプリングと線接触（断面図では点接触）するように、フロント側に突出した断面凸円弧状に形成される。外輪１２の鍔部１２ａは、固定体３０（外側本体３１）とピストン２２のフランジ部２２ｄとの間で作用する予圧スプリング２４によってダイヤフラムスプリングに常時当接している。   The outer ring 12 is a press-formed product of a steel plate, like the inner ring 11, and has a flange 12a that extends to the inner diameter side and abuts against a diaphragm spring (not shown). The flange portion 12a of the outer ring 12 is formed in a convex circular arc shape that protrudes to the front side so as to be in line contact (point contact in the sectional view) with the diaphragm spring. The flange portion 12 a of the outer ring 12 is always in contact with the diaphragm spring by a preload spring 24 that acts between the fixed body 30 (outer body 31) and the flange portion 22 d of the piston 22.

第２シール部材１６は、図２に示すように、芯金１７およびこの表面を被覆するように設けられたゴム製の被覆層１８からなり、芯金１７をインサートして被覆層１８が型成形（加硫成形）されたものである。この第２シール部材１６は、内径端部に形成されたリップを全周に亘って内輪１１の第１鍔部１１ａの端面に接触させるようにして、その外径端部が外輪１２の内径面に圧入固定される。   As shown in FIG. 2, the second seal member 16 includes a cored bar 17 and a rubber coating layer 18 provided so as to cover the surface thereof. The cored layer 17 is inserted to form the coating layer 18. (Vulcanized molding). The second seal member 16 is configured such that the lip formed at the inner diameter end portion contacts the end surface of the first flange portion 11a of the inner ring 11 over the entire circumference, and the outer diameter end portion is the inner diameter surface of the outer ring 12. It is press-fitted and fixed.

第１シール部材１５は、第２シール部材１６と同様に、芯金１７およびこの表面を被覆するように設けられたゴム製の被覆層１８からなり、芯金１７をインサートして被覆層１８が加硫成形されたものである。この第１シール部材１５は、図３にもさらに拡大して示すように、軸方向に延在する略円筒状を呈し、外輪１２の内径面に圧入固定される固定部１５ａと、軸方向に延在する略円筒状を呈し、軸受内方側の一端を内輪１１の外径面に接触させて接触シールＳ１を形成するシール部１５ｂと、半径方向に延在し、固定部１５ａとシール部１５ｂの軸受外方側の一端を連結する基部１５ｃとを備える。   Similar to the second seal member 16, the first seal member 15 includes a cored bar 17 and a rubber coating layer 18 provided so as to cover the surface of the first seal member 15. Vulcanized and molded. As shown in FIG. 3 in an enlarged manner, the first seal member 15 has a substantially cylindrical shape extending in the axial direction, and a fixing portion 15a that is press-fitted and fixed to the inner diameter surface of the outer ring 12, and an axial direction. A substantially cylindrical shape that extends, a seal portion 15b that forms a contact seal S1 with one end on the inner side of the bearing in contact with the outer diameter surface of the inner ring 11, and a fixed portion 15a and a seal portion that extend in the radial direction. And a base portion 15c for connecting one end of the bearing outer side of 15b.

基部１５ｃの半径方向略中央部には、他所よりも軸受外方側（リア側）の端面が軸受外方側に位置する突出部１５ｄが設けられ、該突出部１５ｄの端面１５ｄ１と、これに対向する内輪１１の第２鍔部１１ｂの端面１１ｂ１との間には、軸方向のシール隙間Ｓ２が形成される。本実施形態において、突出部１５ｄは、図４（ａ）に示すように、第１シール部材１５の円周方向全周に亘って形成され、また被覆層１８を形成するのと同時に型成形される。   At the substantially central portion in the radial direction of the base portion 15c, there is provided a projecting portion 15d whose end surface on the bearing outer side (rear side) is located on the bearing outer side with respect to other locations, and an end surface 15d1 of the projecting portion 15d, An axial seal gap S <b> 2 is formed between the end surface 11 b <b> 1 of the second flange portion 11 b of the inner ring 11 that faces the inner ring 11. In the present embodiment, the protrusion 15d is formed over the entire circumference of the first seal member 15 as shown in FIG. 4A, and is molded at the same time as the coating layer 18 is formed. The

突出部１５ｄは、基部１５ｃを構成する被覆層１８の厚みを他所に比べて厚くした肉盛り状の形態をなし、その外径側には、被覆層１８の厚みが突出部１５ｄに比べて薄肉に形成された薄肉部１５ｅが設けられる。薄肉部１５ｅの端面は、当該第１シール部材１５（の外径端部；固定部１５ａ）を外輪１２の内径面に組み込む際に押圧される受圧面とされる。受圧面として機能する薄肉部１５ｅの端面は、軸線と直交する方向の平坦面に形成される。かかる態様の薄肉部１５ｅを設けることにより、外輪１２に対する第１シール部材１５の組み込み性（圧入性）が良好なものとなる。すなわち、仮に基部１５ｃの端面を突出部１５ｄの端面のみで構成すると、突出部１５ｄがゴム材料で比較的厚肉に形成されるが故に、この第１シール部材１５に付与される軸受内方側への押圧力が突出部１５ｄで形成されてしまい、第１シール部材１５を所望の態様で組み込むのが難しくなるおそれがあるからである。ちなみに、本実施形態において、突出部１５ｄにおける被覆層１８の厚みは０．３ｍｍ以上とされる一方、薄肉部１５ｅにおける被覆層１８の厚みは０．１５ｍｍ程度である。   The projecting portion 15d has a built-up form in which the thickness of the covering layer 18 constituting the base portion 15c is made thicker than other portions, and on the outer diameter side, the thickness of the covering layer 18 is thinner than that of the projecting portion 15d. The thin part 15e formed in is provided. The end surface of the thin portion 15e is a pressure receiving surface that is pressed when the first seal member 15 (the outer diameter end portion thereof; the fixed portion 15a) is incorporated into the inner diameter surface of the outer ring 12. The end surface of the thin portion 15e that functions as a pressure receiving surface is formed as a flat surface in a direction orthogonal to the axis. By providing the thin-walled portion 15e in this mode, the assemblability (pressability) of the first seal member 15 with respect to the outer ring 12 is improved. That is, if the end surface of the base portion 15c is constituted only by the end surface of the projecting portion 15d, the projecting portion 15d is formed with a relatively thick wall from a rubber material, so that the bearing inner side applied to the first seal member 15 is provided. This is because the pressing force is formed by the protrusion 15d, and it may be difficult to incorporate the first seal member 15 in a desired manner. Incidentally, in the present embodiment, the thickness of the covering layer 18 in the protruding portion 15d is set to 0.3 mm or more, while the thickness of the covering layer 18 in the thin portion 15e is about 0.15 mm.

なお、第１および第２シール部材１５，１６を構成するゴム製の被覆層１８は、耐摩耗性および耐水性を具備するゴム材料、例えば、ニトリルゴム（ＮＢＲ）、水素添加ニトリルゴム（Ｈ−ＮＢＲ）、耐熱ニトリルゴム、フッ素ゴム（ＦＫＭ）等で形成され、本実施形態では水素添加ニトリルゴムで形成される。   The rubber covering layer 18 constituting the first and second sealing members 15 and 16 is made of a rubber material having wear resistance and water resistance, such as nitrile rubber (NBR), hydrogenated nitrile rubber (H- NBR), heat-resistant nitrile rubber, fluorine rubber (FKM) or the like, and in this embodiment, formed of hydrogenated nitrile rubber.

以上に示すように、内輪１１に外径側に延在する第２鍔部１１ｂを設け、該第２鍔部１１ｂと第１シール部材１５との間に軸方向のシール隙間Ｓ２、すなわち、非接触タイプのシールを形成すれば、外輪１１の回転力（回転に伴って生じる遠心力）によって泥水の浸入量を効果的に低減することができる。仮に、シール隙間Ｓ２を越えて泥水が浸入したとしても、この泥水をシール部１５ｂと内輪１１の外径面との接触部（接触シールＳ１）で捕捉することができる。また、前述のとおり、本発明で付加されるシール機能は、いわゆる非接触シールであるから、軸受トルクを増大させることなく、シール性能の向上が図られる。特に、外径側に開口しているが故に、泥水が跳ね掛けられ易い（侵入し易い）リア側開口部において上記構成を採用したので、シール性能向上を図る上で好適である。   As described above, the inner ring 11 is provided with the second flange part 11b extending to the outer diameter side, and the axial seal gap S2 between the second flange part 11b and the first seal member 15, that is, non- If a contact-type seal is formed, the amount of intrusion of muddy water can be effectively reduced by the rotational force of the outer ring 11 (centrifugal force generated with the rotation). Even if the muddy water enters the seal gap S2, the muddy water can be captured by the contact portion (contact seal S1) between the seal portion 15b and the outer diameter surface of the inner ring 11. Further, as described above, since the sealing function added in the present invention is a so-called non-contact seal, the sealing performance can be improved without increasing the bearing torque. In particular, since the opening is formed on the outer diameter side, the above configuration is adopted in the rear side opening where mud water is likely to splash (easy to enter), which is suitable for improving the sealing performance.

また、シール隙間Ｓ２を、金属材料で形成され、複雑形状を得るのが困難な内輪１１や芯金１７で形成するのではなく、型成形（加硫成形）されるゴム製の突出部１５ｄで形成するようにしたので、上記の効果を奏し得るシール隙間Ｓ２を容易かつ高精度に形成することができる。   Further, the seal gap S2 is not formed by the inner ring 11 or the cored bar 17 which is formed of a metal material and it is difficult to obtain a complicated shape, but is formed by a rubber protruding portion 15d which is molded (vulcanized). Since it is formed, it is possible to easily and highly accurately form the seal gap S2 that can achieve the above effects.

なお、上記のような作用効果を得る上で、シール隙間Ｓ２の隙間幅ｔは、０ｍｍ＜ｔ≦０．８ｍｍ以下に設定するのが望ましい。まず、隙間幅ｔを０ｍｍよりも大きくするのは、非接触シールを構成する上で必須条件である。また、隙間幅ｔを０．８ｍｍ以下とするのは、本願発明者らが鋭意研究を重ねた結果、跳ね掛けられる泥水の粒子（水滴）の直径は、その大半が０．８ｍｍよりも大径であり、この隙間幅を境界として、シール性能が大きく異なることを見出したためである。   In order to obtain the above-described effects, the gap width t of the seal gap S2 is desirably set to 0 mm <t ≦ 0.8 mm or less. First, it is an indispensable condition for making the non-contact seal that the gap width t is larger than 0 mm. In addition, the gap width t is set to 0.8 mm or less, as a result of the present inventors' extensive research, the diameter of muddy water particles (water droplets) splashed is mostly larger than 0.8 mm. This is because it has been found that the sealing performance differs greatly with this gap width as a boundary.

以上では、ゴム製の突出部１５ｄを第１シール部材１５の円周方向全周に亘って設けた場合について説明を行ったが、突出部１５ｄは、図４（ｂ）に示すように、第１シール部材１５の半径方向に対して傾斜した羽根形状とし、かつ第１シール部材１５の円周方向で断続的に複数設けることもできる。この場合、外輪１１の回転時には、送風作用が生じるため、泥水の浸入量を効果的に低減することができる。   In the above, the case where the rubber protruding portion 15d is provided over the entire circumference in the circumferential direction of the first seal member 15 has been described. However, the protruding portion 15d is formed as shown in FIG. A blade shape inclined with respect to the radial direction of one seal member 15 and a plurality of the seal members 15 may be provided intermittently in the circumferential direction of the first seal member 15. In this case, when the outer ring 11 rotates, an air blowing action occurs, so that the amount of muddy water entering can be effectively reduced.

また、以上で説明した実施形態では、突出部１５ｄを、被覆層１８の成形と同時に型成形したが、被覆層１８を成形した後、別工程で肉盛り状に形成することも可能である。かかる構成は、例えば、突出部１５ｄとシール部１５ｂ等とで求められる特性が著しく異なり、被覆層１８の形成材料と突出部１５ｄの形成材料とを異ならせる必要が生じる場合等に有効である。   Further, in the embodiment described above, the projecting portion 15d is molded at the same time as the coating layer 18 is molded. However, after the coating layer 18 is molded, it can be formed in a built-up shape in a separate process. Such a configuration is effective when, for example, the required characteristics of the protruding portion 15d and the seal portion 15b are significantly different, and it is necessary to make the forming material of the coating layer 18 different from the forming material of the protruding portion 15d.

また、以上で説明した実施形態では、軸方向のシール隙間Ｓ２を、第１シール部材１５（の突出部１５ｄ）と、内側部材としての内輪１１に設けた第２鍔部１１ｂとの間に形成しているが、本発明はかかる形態に限定されない。例えば図５に示すように、内側部材に設けるべき鍔部を、内輪１１のリア側一端に固定したカバー材１９で構成し、このカバー材１９と、第１シール部材１５（の突出部１５ｄ）との間に軸方向のシール隙間Ｓ２を形成することもできる。   In the embodiment described above, the axial seal gap S2 is formed between the first seal member 15 (the protruding portion 15d thereof) and the second flange portion 11b provided on the inner ring 11 as the inner member. However, the present invention is not limited to such a form. For example, as shown in FIG. 5, the collar portion to be provided on the inner member is constituted by a cover material 19 fixed to one end on the rear side of the inner ring 11, and this cover material 19 and the first seal member 15 (protruding portion 15d) An axial seal gap S2 can also be formed between the two.

以上、本発明について説明を行ったが、本発明は上述した実施形態に何ら限定されるものでなく、本発明の要旨を逸脱しない範囲において、さらに種々なる形態で実施し得ることは勿論のことである。本発明の範囲は、特許請求の範囲によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内の全ての変更を含む。   The present invention has been described above. However, the present invention is not limited to the above-described embodiment, and can of course be implemented in various forms without departing from the gist of the present invention. It is. The scope of the present invention is defined by the terms of the claims, and includes the equivalent meanings recited in the claims and all modifications within the scope.

本発明の有用性を実証するため、耐泥水性に関する確認試験を以下示す条件で行った。耐泥水性は、軸受の内部容積に占める水の割合（含水率）で評価するものとし、その試験結果を図６に示す。試験体は、シール隙間Ｓ２を設けていないもの（比較例１）、およびシール隙間Ｓ２の隙間幅を０．９ｍｍとしたもの（比較例２）、およびシール隙間Ｓ２の隙間幅を０．８ｍｍ（実施例１）、０．４８ｍｍ（実施例２）としたものの４種である。なお、比較例２および実施例１は、図４（ａ）に示す形態の突出部１５ｄを設けたものであり、実施例２は図４（ｂ）に示す形態の突出部１５ｄを設けたものである。
［試験条件］
（１）回転速度：３０００ｒ／ｍｉｎ
（２）負荷荷重：８０Ｎ〜２２５３Ｎ
（３）起動停止のサイクル：起動時間１３．２ｓｅｃ、停止時間１．８ｓｅｃ
（４）泥水条件：ＪＩＳ８種 関東ローム層の土を１５ｗｔ％含有
（５）試験時間：５０ｍｉｎ In order to demonstrate the usefulness of the present invention, a confirmation test regarding mud water resistance was performed under the following conditions. The mud water resistance is evaluated by the ratio of water (water content) to the internal volume of the bearing, and the test results are shown in FIG. The test specimens have no seal gap S2 (Comparative Example 1), the seal gap S2 has a gap width of 0.9 mm (Comparative Example 2), and the seal gap S2 has a gap width of 0.8 mm ( Example 1) and 0.48 mm (Example 2). Note that Comparative Example 2 and Example 1 are provided with a protrusion 15d having the form shown in FIG. 4A, and Example 2 is provided with a protrusion 15d having the form shown in FIG. 4B. It is.
[Test conditions]
(1) Rotational speed: 3000 r / min
(2) Load load: 80N to 2253N
(3) Start-stop cycle: Start-up time 13.2 sec, stop time 1.8 sec
(4) Muddy water conditions: JIS type 8 containing 15 wt% soil of Kanto Loam layer (5) Test time: 50 min

図６に示す試験結果からも明らかなように、比較例１および比較例２では、十分な耐泥水性（シール性）を確保することができなかったのに対し、本発明に係る実施例１および実施例２では、十分なシール性を確保することができた。従って、本発明の有用性が確認できる。   As is clear from the test results shown in FIG. 6, in Comparative Example 1 and Comparative Example 2, sufficient muddy water resistance (sealability) could not be secured, whereas Example 1 according to the present invention. And in Example 2, sufficient sealing performance could be secured. Therefore, the usefulness of the present invention can be confirmed.

クラッチレリーズ軸受を組み込んだクラッチレリーズ軸受装置の全体構成を示す断面図である。It is sectional drawing which shows the whole structure of the clutch release bearing apparatus incorporating a clutch release bearing. 本発明の第１実施形態に係るクラッチレリーズ軸受の断面図である。It is sectional drawing of the clutch release bearing which concerns on 1st Embodiment of this invention. 図２の要部拡大断面図である。It is a principal part expanded sectional view of FIG. 第１シール部材をリア側から見た平面図であり、（ａ）図は、突出部を全周に亘って設けた場合を示す平面図、（ｂ）図は、突出部を円周方向で断続的に設けた場合を示す平面図である。It is the top view which looked at the 1st seal member from the rear side, (a) Drawing is a top view showing the case where a projection part is provided over the perimeter, (b) Drawing is a projection part in the circumference direction It is a top view which shows the case where it provides intermittently. 本発明の第２実施形態に係るクラッチレリーズ軸受の断面図である。It is sectional drawing of the clutch release bearing which concerns on 2nd Embodiment of this invention. 本発明の有用性を実証するための確認試験結果を示す図である。It is a figure which shows the confirmation test result for demonstrating the usefulness of this invention.

符号の説明Explanation of symbols

１ クラッチレリーズ軸受装置
１０ クラッチレリーズ軸受
１１ 内輪（内側部材）
１２ 外輪（外側部材）
１３ ボール（転動体）
１４ 保持器
１５ 第１シール部材
１５ｄ 突出部
１５ｅ 薄肉部
１６ 第２シール部材
１７ 芯金
１８ 被覆層
２０ 可動体
２１ ピストン支持チューブ
２２ ピストン
２３ 皿ばね
２４ 予圧スプリング
３０ 固定体
４０ 容積可変チャンバ
Ｓ１ 接触シール
Ｓ２ 軸方向のシール隙間 1 Clutch release bearing device 10 Clutch release bearing 11 Inner ring (inner member)
12 Outer ring (outer member)
13 balls (rolling elements)
DESCRIPTION OF SYMBOLS 14 Cage 15 1st seal member 15d Protrusion part 15e Thin part 16 2nd seal member 17 Core metal 18 Coating layer 20 Movable body 21 Piston support tube 22 Piston 23 Disc spring 24 Preload spring 30 Fixed body 40 Volume variable chamber S1 Contact seal S2 Axial seal gap

Claims (6)

クラッチ装置の回転部材との当接部を有する回転側の外側部材と、外側部材の内周に配設された静止側の内側部材と、外側部材と内側部材の間に介在する複数の転動体と、外径端部が外側部材の内径面に固定されると共に、内径端部が内側部材の外径面に接触して、外側部材と内側部材との間を密封するシール部材とを備えるクラッチレリーズ軸受において、
内側部材に外径側に延在する鍔部を設け、該鍔部とシール部材との間に軸方向のシール隙間を形成したことを特徴とするクラッチレリーズ軸受。 A rotating-side outer member having a contact portion with a rotating member of the clutch device, a stationary-side inner member disposed on the inner periphery of the outer member, and a plurality of rolling elements interposed between the outer member and the inner member And a seal member that has an outer diameter end fixed to the inner diameter surface of the outer member and a seal member that contacts the outer diameter surface of the inner member and seals between the outer member and the inner member. In release bearings,
A clutch release bearing characterized in that an inner member is provided with a flange extending to the outer diameter side, and an axial seal gap is formed between the flange and the seal member. シール隙間の隙間幅ｔを、０ｍｍ＜ｔ≦０．８ｍｍとした請求項１記載のクラッチレリーズ軸受。   The clutch release bearing according to claim 1, wherein a gap width t of the seal gap is set to 0 mm <t ≦ 0.8 mm. シール部材にゴム製の突出部を設け、該突出部の一端面と鍔部の対向面との間にシール隙間を形成した請求項１又は２記載のクラッチレリーズ軸受。   The clutch release bearing according to claim 1 or 2, wherein a rubber protrusion is provided on the seal member, and a seal gap is formed between one end surface of the protrusion and the opposing surface of the flange. 突出部が、シール部材の円周方向全周に亘って設けられた請求項３記載のクラッチレリーズ軸受。   The clutch release bearing according to claim 3, wherein the projecting portion is provided over the entire circumference of the seal member in the circumferential direction. 突出部が、半径方向に対して傾斜した羽根形状を呈し、かつシール部材の円周方向で断続的に複数設けられた請求項３記載のクラッチレリーズ軸受。   The clutch release bearing according to claim 3, wherein the protrusion has a blade shape inclined with respect to the radial direction, and a plurality of the protrusions are provided intermittently in a circumferential direction of the seal member. シール部材は、芯金およびこれを被覆するゴム製の被覆層からなり、該被覆層は、その一部に形成した突出部の外径側に、外側部材への組み込み時に押圧される受圧面を有する請求項３記載のクラッチレリーズ軸受。   The sealing member is composed of a cored bar and a rubber coating layer that covers the core metal, and the coating layer has a pressure receiving surface that is pressed on the outer diameter side of the protruding portion formed in a part thereof when being assembled into the outer member. The clutch release bearing according to claim 3.
JP2007325814A 2007-12-18 2007-12-18 Clutch release bearing Withdrawn JP2009144895A (en)

Priority Applications (1)

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Application Number Priority Date Filing Date Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015093376A1 (en) 2013-12-16 2015-06-25 日本精工株式会社 Release bearing and clutch release bearing device
DE102016204500B3 (en) * 2016-03-18 2017-08-03 Schaeffler Technologies AG & Co. KG release bearing

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015093376A1 (en) 2013-12-16 2015-06-25 日本精工株式会社 Release bearing and clutch release bearing device
KR20160074625A (en) 2013-12-16 2016-06-28 닛본 세이고 가부시끼가이샤 Release bearing and clutch release bearing device
US10006503B2 (en) 2013-12-16 2018-06-26 Nsk Ltd. Release bearing and clutch release bearing device
EP3674575A1 (en) 2013-12-16 2020-07-01 NSK Ltd. Clutch release bearing device
DE102016204500B3 (en) * 2016-03-18 2017-08-03 Schaeffler Technologies AG & Co. KG release bearing
US10473155B2 (en) 2016-03-18 2019-11-12 Schaeffler Technologies AG & Co. KG Release bearing

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