WO2019172122A1 - Clutch release bearing device - Google Patents
Clutch release bearing device Download PDFInfo
- Publication number
- WO2019172122A1 WO2019172122A1 PCT/JP2019/008111 JP2019008111W WO2019172122A1 WO 2019172122 A1 WO2019172122 A1 WO 2019172122A1 JP 2019008111 W JP2019008111 W JP 2019008111W WO 2019172122 A1 WO2019172122 A1 WO 2019172122A1
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- WO
- WIPO (PCT)
- Prior art keywords
- release bearing
- clutch
- spring
- diaphragm spring
- bearing device
- Prior art date
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Classifications
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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
- F16D23/143—Arrangements or details for the connection between the release bearing and the diaphragm
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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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
- F16D13/71—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members in which the clutching pressure is produced by springs only
Definitions
- the present invention relates to a clutch release bearing device that is disposed between an engine and a transmission of an automobile and transmits / cuts power from the engine to the transmission.
- the automobile clutch mechanism is located between the engine and the transmission, and functions to transmit or disconnect the engine output to the drive system after the transmission.
- a manual transmission As shown in FIG. 5, there is a flywheel 33 on the engine side, a pressure plate 42 on the transmission side, and a clutch disk 44 with a friction material attached between them.
- the pressure force of the diaphragm spring 40 causes the pressure plate 42 to press the clutch disc 44 against the flywheel 33 to generate a frictional force, and the power from the engine output shaft 50 is transmitted.
- the clutch disc 44 When the diaphragm spring 40 is pushed, the clutch disc 44 is separated from the flywheel 33 and the clutch is cut off.
- the clutch release bearing device A functions to push the diaphragm spring 40 when the clutch is cut off.
- the clutch release bearing device A slides on the front cover 34 by a release fork 32 interlocked with a clutch pedal (not shown).
- the front cover 34 is attached to a transmission clutch case 36, and an input shaft 38 of the transmission passes through the inside of the front cover 34.
- the clutch release bearing device A is separated from the diaphragm spring 40, and the pressure plate 42 is pressed against the clutch disc 44 of the flywheel 46 by the action of the diaphragm spring 40, that is, the output shaft of the engine.
- the power from 50 is transmitted.
- the release fork 32 swings counterclockwise in FIG. 5 and presses the clutch release bearing device A against the diaphragm spring 40.
- the diaphragm spring 40 is bent, the pressure plate 42 is separated from the clutch disk 44, the clutch is disengaged, and the power from the engine output shaft 50 is cut off.
- the diaphragm spring 40 has an annular circular base portion 40a that abuts on the pressure plate 42, and is gradually curved from the circular base portion 40a toward the transmission side so as to end on the transmission side. Consists of a plurality of spring teeth 40b provided radially so as to surround the front cover 34.
- Patent Documents 1 to 5 There are self-aligning type clutch release bearing devices A (Patent Documents 1 to 5).
- the self-aligning type clutch release bearing device A includes a sleeve 27 that slides on the front cover 34 in the axial direction, and a release bearing 28 that is attached to the outer periphery of the sleeve 27.
- the release bearing 28 includes an inner ring 28a, an outer ring 28b, a rolling element 28c, and a cage 28d.
- Patent Documents 4 and 5 describe that a diaphragm spring is pressed by a pressing member (buffer material) fixed to a release bearing. And it is disclosed that a plastic material is used as the pressing member.
- the diaphragm spring 40 is configured by a plurality of spring teeth 40b radially provided so as to surround the front cover. However, there is a variation in the axial position of the tip between the spring teeth 40b. Has occurred.
- the present invention is intended to reduce the wear of the cushioning material sandwiched between the diaphragm spring and the release bearing.
- the present invention provides a clutch release bearing device including a release bearing that presses a diaphragm spring having a plurality of spring teeth in the circumferential direction in the axial direction through a resin cushioning material. A gap is provided between the material and the inner ring.
- the buffer material can be attached to a pressing member that presses the diaphragm spring of the release bearing.
- the cushioning material is prevented from rotating in the circumferential direction with respect to the release bearing.
- the gap between the cushioning material and the inner ring is located at the position closest to the outer peripheral edge and the axial height of the spring teeth located farthest from the outer peripheral edge of the diaphragm spring with respect to the outer peripheral edge. It is set to be larger than the difference between the axial height of a certain spring tooth with respect to the outer peripheral edge.
- the clutch release bearing device by providing a gap between the cushioning material and the release bearing, when the diaphragm bearing is pressed against the diaphragm spring, a large surface pressure is hardly generated on the cushioning material. Wear can be suppressed.
- FIG. 5 is a cross-sectional view of the clutch release bearing device according to the embodiment of the present invention cut along A-A ′ of the side plate shown in FIG. 4.
- FIG. 2 is an enlarged view showing the periphery of an inner ring that presses a diaphragm spring in the clutch release bearing device of FIG. 1. It is a side view of the inner ring
- (A) is sectional drawing of the XX line of (b),
- (b) is a side view of a diaphragm spring.
- FIG. 8 is an enlarged view of the clutch release bearing device of FIG. 7 in which the inner ring is pressed against the diaphragm by a cushioning material. It is an enlarged view which shows the inner ring periphery which presses the diaphragm spring in the clutch release bearing apparatus of the reference example relevant to this invention.
- FIG. 5 the right side of the drawing may be referred to as one axial side (transmission side), and the left side of the drawing may be referred to as the other axial side (engine side).
- the clutch release bearing device A is attached to the outer periphery of the front cover 34 of the clutch case 36 through which the input shaft 38 of the transmission penetrates so as to be slidable in the axial direction.
- the front cover 34 is slid in the axial direction toward the other side (engine side) in the axial direction and the diaphragm spring 40 of the clutch device B is pressed, whereby the diaphragm spring 40 is bent and the pressure plate 42 is clutched.
- the clutch is disengaged away from the disk 44, and the power from the engine output shaft 50 is cut off.
- a sleeve 1, a release bearing 2 fitted on the sleeve 1, and a clutch release fork 32 (see FIG. 5) abut.
- a substantially disc-shaped side plate 3, an elastic member 4 that applies a predetermined axial load to the release bearing 2, and a sleeve 1, the release bearing 2, the side plate 3, and a cover 5 that holds the elastic member 4 are provided.
- the clutch release bearing device A causes the release bearing 2 to move in the radial direction according to the amount of displacement when a displacement occurs between the engine-side shaft center and the transmission-side shaft center. It is a self-aligning type that automatically aligns the misalignment between the two axes by sliding.
- the sleeve 1 is a sleeve that is slidable in the axial direction on the front cover 34 protruding from the clutch cover 36 of the transmission, and has a cylindrical shape.
- the sleeve 1 is made of a resin, for example, a thermoplastic synthetic resin such as PA (polyamide) 66.
- the resin material forming the sleeve 1 may contain 5 to 25 wt% of a reinforcing material such as carbon fiber.
- the release bearing 2 includes an outer ring 6, an inner ring 7, a cage 8, and rolling elements 9.
- the release bearing 2 is externally fitted to the sleeve 1 via a predetermined radial gap S1.
- the outer ring 6 has an outer raceway surface 6a on the inner periphery.
- the inner ring 7 is provided on the inner diameter side of the outer ring 6, and has an inner raceway surface 7a facing the outer raceway surface 6a on the outer periphery.
- the inner ring 7 is cylindrical.
- the inner ring 7 is formed with an extended portion 7 b that extends outward in the axial direction from the axial end surface (protective cover 5) of the outer ring 6 at the axial end on the diaphragm spring 40 side.
- the inner ring 7 has the inner ring raceway surface 7a and the main body portion having substantially the same axial dimension as the outer ring 6, and the other axial end side of the main body portion (the other axial end surface of the outer ring 6). And an extended portion (a protruding portion protruding to the other side in the axial direction (engine side)).
- a plurality of rolling elements (balls) 9 are accommodated via a cage 8 so as to be able to roll.
- Seals 10 and 11 are attached to both ends of the outer ring 6. The seals 10 and 11 prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater and dust from the outside into the bearing.
- the inner ring 7 is externally attached to the sleeve 1, and when a clutch pedal (not shown) is stepped on, an extension portion 7 b extending in the axial direction toward the diaphragm spring 40 side is provided radially so as to surround the front cover 34.
- the spring teeth 40b of the diaphragm spring 40 are pressed in the axial direction via a cushioning material 31 to be described later, the pressure plate 42 is separated from the clutch disk 44 by the bending of the diaphragm spring 40, and the power from the engine output shaft 50 is transmitted to the transmission. Temporarily disconnected from.
- the inner ring 7 is a pressing member that presses the diaphragm spring 40.
- the pressing member may be an outer ring or may be a separate member that is press-fitted into the inner ring inner diameter.
- the diaphragm spring 40 is a disk-shaped member disposed between the pressure plate 42 and the clutch cover 45.
- the diaphragm spring 40 has an annular circular base portion 40a that contacts the pressure plate 42, and spring teeth 40b that extend radially inward from the inner peripheral portion of the circular base portion 40a.
- the circular base 40a abuts the pressure plate 42 on the flywheel 33 side.
- a slit is formed between the spring teeth 40b.
- the side plate 3 is a substantially circular plate and is formed by pressing a steel plate material.
- the side plate 3 uses a carburized steel plate as a steel plate material.
- the material of the steel plate forming the side plate 3 is SCM (chromium molybdenum steel).
- SCM chromium molybdenum steel
- the cold-rolled steel sheet made of SCM is formed into a predetermined shape by pressing.
- the side plate 3 is integrated with the resin sleeve 1 by insert molding.
- the side plate 3 is formed with a main body portion 3a that engages with and guides the clutch release fork 32.
- the side plate 3 has a flange 3c that extends from the inner diameter edge of the main body 3a to one side in the axial direction (transmission side).
- the collar portion 3 c is embedded in the sleeve 1.
- An inner diameter portion 3b embedded in the sleeve 1 is constituted by a part of the main body portion 3a and the flange portion 3c.
- the collar portion 3c is provided with a notch portion 3d having a function of preventing the side plate 3 from rotating with respect to the sleeve 1.
- the flange portion 3c may extend from the inner diameter edge of the main body portion 3a to the other side in the axial direction (engine side).
- the elastic member 4 is, for example, a disc spring of a steel plate press-formed product.
- the elastic member 4 is composed of a plurality of end rings having a flat cross section, for example, 3 to 5 waves, and corrugated and rounded from a wire such as a steel wire (JIS standard SW, SWP system). After being molded and subjected to strain relief annealing by heat treatment, age hardening treatment is performed.
- the cover 5 is formed in a cylindrical shape that covers the release bearing 2 by pressing a steel plate having corrosion resistance, for example, a cold rolled steel plate (JIS standard SPCC system) or an austenitic stainless steel sheet (JIS standard SUS304 system). Is formed.
- the cover 5 has an inner flange 5a for accommodating the elastic member 4 at one end, and tongues 5b at a plurality of locations in the circumferential direction at the other end.
- the tongue piece 5b is crimped to the outer diameter portion of the side plate 3 and is held so that the elastic member 4, the outer ring 6, and the side plate 3 are not separated.
- the cover 5 Since the elastic member 4 does not slide between the inner flange 5a of the cover 5, the cover 5 will not be unevenly worn. Therefore, a predetermined holding force can be maintained and the release bearing 2 can be stably held at the alignment position for a long period of time.
- the outer ring 6 of the release bearing 2 is elastically held by the elastic member 4 formed of a ring having a plurality of waves, and the release bearing 2 is fitted on the sleeve 1 via a predetermined radial gap. ing.
- a radial clearance S1 is provided between the outer periphery of the sleeve 1 and the inner periphery of the inner ring 7 of the release bearing 2, and between the outer periphery of the outer ring 6 of the release bearing 2 and the inner periphery of the cover 5, A radial clearance S2 smaller than the radial clearance S1 is provided.
- the outer ring 6 is elastically pressed against the end surface of the side plate 3 by the biasing force of the elastic member 4 interposed between the outer ring 6 and the inner side surface of the cover 5.
- the release bearing 2 is elastically held between the outer periphery of the sleeve 1 and the end face of the side plate 3 so as to be slidable in the radial direction, that is, floatable.
- the release bearing 2 can be aligned in the radial direction with respect to the sleeve 1 and the side plate 3 by the radial clearances S1 and S2, and the alignment movement amount is regulated by the smaller radial clearance S2.
- the extension provided at the axial end of the inner ring 7 of the release bearing 2 on the diaphragm spring 40 side.
- An annular cushioning material 31 is provided between 7 b and the spring teeth 40 b of the diaphragm spring 40.
- the buffer material 31 is a resin material made of polyamide resin, and is attached to the extension portion 7b of the inner ring 7 by vulcanization adhesion.
- the cushioning material 31 has an annular portion 31a that contacts the diaphragm 40, and a convex portion 31b that engages with a concave portion 7c of an extension portion 7b described later. Since the inner diameter of the cushioning material 31 is smaller than the inner diameter of the inner ring 7, the thickness of the convex portion 31b becomes equal to the thickness of the annular portion 31a, and the cushioning material 31 is easily vulcanized and bonded to the extension portion 7b.
- the gap S3 includes an axial height Lmax of the spring tooth 40b1 that is farthest from the outer peripheral edge of the diaphragm spring 40 (the circular base part 40a) of the plurality of spring teeth 40b, and the circular base part 40a. This is larger than the difference between the spring tooth 40b2 located closest to the outer peripheral edge and the axial height Lmin relative to the outer peripheral edge.
- the distance from the imaginary line V extending in the direction orthogonal to the axial direction through the outer peripheral edge of the circular base 40a to the tip edges of the spring teeth 40b1 and 40b2 is expressed as “ It is defined as "the axial height of the spring teeth 40b".
- the cushioning material 31 is attached to the inner ring 7 that presses the diaphragm spring 40, wear of the cushioning material 31 can be prevented with a simple and compact structure.
- the buffer material 31 may be attached to the diaphragm spring 40 side.
- the clearance S3 is provided between the buffer material 31 and the inner ring 7, so that wear of the buffer material 31 due to vibration can be suppressed.
- the buffer material 31 may rotate in the circumferential direction with respect to the inner ring 7.
- the extension part 7 b of the inner ring 7 is provided with a recess 7 c for preventing rotation.
- the recess 7c is formed by denting a part of the inner peripheral surface of the extension 7b to the outer diameter side.
- the inner ring 7 is provided with a plurality of recesses 7c so as to face each other across the center O.
- the convex part provided in the extension part 7b may be engaged with the concave part provided in the buffer material 31, or both the concave part and the convex part are provided in the buffer material 31 and the extension part 7b, respectively. You may make it match.
- the clutch release bearing device shown in FIG. 9 has a release bearing 2A that presses a diaphragm spring 40 having a plurality of spring teeth 40b in the circumferential direction in the axial direction, and an extension 7Ab provided on the inner ring 7 of the release bearing 2A.
- the buffer material 31A is a rubber material.
- a separate cushioning material 31 ⁇ / b> A is provided between the diaphragm spring 40 and the inner ring 7.
- the buffer material 31 ⁇ / b> A has a ring shape, and the buffer material 31 ⁇ / b> A is vulcanized and bonded to the extension 7 ⁇ / b> Ab of the inner ring 7.
- the buffer material 31A is, for example, a rubber material such as nitrile rubber (NBR), acrylic rubber (ACM), or vinylidene fluoride rubber (FKM).
- the spring teeth 40b and the extension portion 7Ab of the release bearing 2A are designed so that one is a line and the other is an arc so as to be in line contact with each other in the circumferential direction. Since it deforms along both shapes, the design can be made independent of the shape.
- Sleeve 2 Release bearing 6: Outer ring 7: Inner ring 7b: Extension part 31: Buffer material 40: Diaphragm spring 40b: Spring tooth A: Self-aligning clutch release bearing device B: Clutch device S3: Clearance
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The present invention addresses the problem of reducing wear of a cushioning material sandwiched between a diaphragm spring and a release bearing in a clutch release bearing device. This clutch release bearing device is provided with a release bearing 2 which presses, by way of a cushioning material 31 made of resin, a diaphragm spring 40 having a plurality of spring teeth 40b in a circumferential direction, and is characterized in that when the release bearing 2 is not pressing the diaphragm spring 40, a gap S3 is provided between the cushioning material 31 and the release bearing 2.
Description
この発明は、自動車のエンジンとトランスミッションとの間に配置され、エンジンからトランスミッションへの動力の伝達・遮断を行うクラッチレリーズ軸受装置に関する。
The present invention relates to a clutch release bearing device that is disposed between an engine and a transmission of an automobile and transmits / cuts power from the engine to the transmission.
自動車のクラッチ機構は、エンジンとトランスミッションとの間にあって、エンジンの出力をトランスミッション以降の駆動系に伝えたり切り離したりする働きをする。
The automobile clutch mechanism is located between the engine and the transmission, and functions to transmit or disconnect the engine output to the drive system after the transmission.
マニュアルトランスミッション(MT)の場合、図5に示すように、エンジン側にフライホイール33、トランスミッション側にプレッシャプレート42があり、両者の間に摩擦材を貼り付けたクラッチディスク44がある。ダイヤフラムスプリング40のばね力でプレッシャプレート42がクラッチディスク44をフライホイール33に押し付け、摩擦力が発生し、エンジンの出力軸50からの動力が伝えられる。ダイヤフラムスプリング40を押すと、クラッチディスク44がフライホイール33から離れてクラッチが遮断され、このクラッチ遮断時にダイヤフラムスプリング40を押す働きをするのがクラッチレリーズ軸受装置Aである。
In the case of a manual transmission (MT), as shown in FIG. 5, there is a flywheel 33 on the engine side, a pressure plate 42 on the transmission side, and a clutch disk 44 with a friction material attached between them. The pressure force of the diaphragm spring 40 causes the pressure plate 42 to press the clutch disc 44 against the flywheel 33 to generate a frictional force, and the power from the engine output shaft 50 is transmitted. When the diaphragm spring 40 is pushed, the clutch disc 44 is separated from the flywheel 33 and the clutch is cut off. The clutch release bearing device A functions to push the diaphragm spring 40 when the clutch is cut off.
クラッチレリーズ軸受装置Aは、図5に示すように、クラッチペダル(図示省略)と連動するレリーズフォーク32によって、フロントカバー34上をスライドする。フロントカバー34はトランスミッションのクラッチケース36に取り付けてあり、フロントカバー34の内部をトランスミッションのインプットシャフト38が貫通している。常時は、クラッチレリーズ軸受装置Aがダイヤフラムスプリング40から離れており、ダイヤフラムスプリング40の作用でプレッシャプレート42を、フライホイール46のクラッチディスク44に押し付けてクラッチが入った状態、即ち、エンジンの出力軸50からの動力が伝達される状態にある。そして、クラッチペダルを踏み込むと、レリーズフォーク32が図5の反時計方向に揺動し、クラッチレリーズ軸受装置Aをダイヤフラムスプリング40に押し付ける。これにより、ダイヤフラムスプリング40が撓み、プレッシャプレート42がクラッチディスク44から離れて、クラッチが切れ、エンジンの出力軸50からの動力が遮断される状態になる。
As shown in FIG. 5, the clutch release bearing device A slides on the front cover 34 by a release fork 32 interlocked with a clutch pedal (not shown). The front cover 34 is attached to a transmission clutch case 36, and an input shaft 38 of the transmission passes through the inside of the front cover 34. Normally, the clutch release bearing device A is separated from the diaphragm spring 40, and the pressure plate 42 is pressed against the clutch disc 44 of the flywheel 46 by the action of the diaphragm spring 40, that is, the output shaft of the engine. The power from 50 is transmitted. When the clutch pedal is depressed, the release fork 32 swings counterclockwise in FIG. 5 and presses the clutch release bearing device A against the diaphragm spring 40. As a result, the diaphragm spring 40 is bent, the pressure plate 42 is separated from the clutch disk 44, the clutch is disengaged, and the power from the engine output shaft 50 is cut off.
ダイヤフラムスプリング40は、図6(a)、(b)に示すように、プレッシャプレート42に当接する環状の円形基部40aと、この円形基部40aからトランスミッション側に次第に湾曲して、トランスミッション側の端部がフロントカバー34を囲むように放射状に設けられた複数のスプリング歯40bとからなる。
As shown in FIGS. 6A and 6B, the diaphragm spring 40 has an annular circular base portion 40a that abuts on the pressure plate 42, and is gradually curved from the circular base portion 40a toward the transmission side so as to end on the transmission side. Consists of a plurality of spring teeth 40b provided radially so as to surround the front cover 34.
このクラッチレリーズ軸受装置Aとして、自動調心型のものがある(特許文献1~5)。
There are self-aligning type clutch release bearing devices A (Patent Documents 1 to 5).
自動調心型のクラッチレリーズ軸受装置Aは、フロントカバー34上を軸方向にスライドするスリーブ27と、スリーブ27の外周に取り付けた、レリーズ軸受28とを備えている。レリーズ軸受28は、内輪28aと、外輪28bと、転動体28cと、保持器28dとからなる。
The self-aligning type clutch release bearing device A includes a sleeve 27 that slides on the front cover 34 in the axial direction, and a release bearing 28 that is attached to the outer periphery of the sleeve 27. The release bearing 28 includes an inner ring 28a, an outer ring 28b, a rolling element 28c, and a cage 28d.
ところで、クラッチレリーズ軸受装置はダイヤフラムと当接する際に、スティックスリップ音が発生する可能性があると共に、クラッチレリーズ軸受装置のうちダイヤフラムと当接する当接面に摩耗が発生する可能性もある。特許文献4および特許文献5には、レリーズ軸受に固定された押圧部材(緩衝材)によってダイヤフラムスプリングを押圧していることが記載されている。そして、押圧部材としては、プラスチック材料を使用することが開示されている。
ここで、ダイヤフラムスプリング40は、上述のとおり、フロントカバーを囲むように放射状に設けられた複数のスプリング歯40bによって構成されているが、各スプリング歯40b間で、その先端の軸方向位置にバラツキが生じている。よって、各スプリング歯40b間では、ダイヤフラムスプリング40の外周縁に対するスプリング歯40bの軸方向高さに寸法差が生じている。この寸法差が存在した状態で押圧部材310をスプリング歯40bに当接させると寸法差の全てを吸収することができず、一部のスプリング歯40bと押圧部材310との当接部に過大な荷重が発生してしまい、押圧部材310が早期に摩耗する可能性がある。この課題は、ダイヤフラムスプリングに限らず、レリーズ軸受のうちダイヤフラムスプリングを押し付ける押付面に寸法差が生じた場合にも同様に生じる。 By the way, when the clutch release bearing device comes into contact with the diaphragm, there is a possibility that a stick-slip noise is generated, and in the clutch release bearing device, there is a possibility that wear occurs on the contact surface that comes into contact with the diaphragm.Patent Documents 4 and 5 describe that a diaphragm spring is pressed by a pressing member (buffer material) fixed to a release bearing. And it is disclosed that a plastic material is used as the pressing member.
Here, as described above, thediaphragm spring 40 is configured by a plurality of spring teeth 40b radially provided so as to surround the front cover. However, there is a variation in the axial position of the tip between the spring teeth 40b. Has occurred. Therefore, there is a dimensional difference between the spring teeth 40b in the axial height of the spring teeth 40b with respect to the outer peripheral edge of the diaphragm spring 40. If the pressing member 310 is brought into contact with the spring teeth 40b in a state where this dimensional difference exists, the entire dimensional difference cannot be absorbed, and the contact portion between some of the spring teeth 40b and the pressing member 310 is excessive. A load may be generated, and the pressing member 310 may be worn early. This problem occurs not only in the diaphragm spring but also in the case where a dimensional difference occurs on the pressing surface of the release bearing that presses the diaphragm spring.
ここで、ダイヤフラムスプリング40は、上述のとおり、フロントカバーを囲むように放射状に設けられた複数のスプリング歯40bによって構成されているが、各スプリング歯40b間で、その先端の軸方向位置にバラツキが生じている。よって、各スプリング歯40b間では、ダイヤフラムスプリング40の外周縁に対するスプリング歯40bの軸方向高さに寸法差が生じている。この寸法差が存在した状態で押圧部材310をスプリング歯40bに当接させると寸法差の全てを吸収することができず、一部のスプリング歯40bと押圧部材310との当接部に過大な荷重が発生してしまい、押圧部材310が早期に摩耗する可能性がある。この課題は、ダイヤフラムスプリングに限らず、レリーズ軸受のうちダイヤフラムスプリングを押し付ける押付面に寸法差が生じた場合にも同様に生じる。 By the way, when the clutch release bearing device comes into contact with the diaphragm, there is a possibility that a stick-slip noise is generated, and in the clutch release bearing device, there is a possibility that wear occurs on the contact surface that comes into contact with the diaphragm.
Here, as described above, the
そこで、この発明は、ダイヤフラムスプリングとレリーズ軸受との間に挟む緩衝材の摩耗を低減しようとするものである。
Therefore, the present invention is intended to reduce the wear of the cushioning material sandwiched between the diaphragm spring and the release bearing.
前記の課題を解決するために、この発明は、周方向に複数のスプリング歯を有するダイヤフラムスプリングを樹脂製の緩衝材を介して軸方向に押し付けるレリーズ軸受を備えたクラッチレリーズ軸受装置において、前記緩衝材と前記内輪との間に隙間が設けられていることを特徴とする。
In order to solve the above problems, the present invention provides a clutch release bearing device including a release bearing that presses a diaphragm spring having a plurality of spring teeth in the circumferential direction in the axial direction through a resin cushioning material. A gap is provided between the material and the inner ring.
前記緩衝材は、前記レリーズ軸受のうち前記ダイヤフラムスプリングを押し付ける押付部材に取り付けることができる。
The buffer material can be attached to a pressing member that presses the diaphragm spring of the release bearing.
前記緩衝材は、前記レリーズ軸受に対し周方向に回り止めされていることが好ましい。
It is preferable that the cushioning material is prevented from rotating in the circumferential direction with respect to the release bearing.
前記緩衝材と前記内輪との間の隙間は、前記ダイヤフラムスプリングの外周縁に対して最も離れた位置にあるスプリング歯の当該外周縁に対する軸方向高さと、前記外周縁に対して最も近い位置にあるスプリング歯の当該外周縁に対する軸方向高さとの差よりも大きく設定されている。
The gap between the cushioning material and the inner ring is located at the position closest to the outer peripheral edge and the axial height of the spring teeth located farthest from the outer peripheral edge of the diaphragm spring with respect to the outer peripheral edge. It is set to be larger than the difference between the axial height of a certain spring tooth with respect to the outer peripheral edge.
以上のように、クラッチレリーズ軸受装置において、緩衝材とレリーズ軸受との間に隙間を設けることで、ダイヤフラムスプリングをレリーズ軸受が押し付けるときに、緩衝材に大きな面圧が生じにくくなり、緩衝材の摩耗を抑制することができる。
As described above, in the clutch release bearing device, by providing a gap between the cushioning material and the release bearing, when the diaphragm bearing is pressed against the diaphragm spring, a large surface pressure is hardly generated on the cushioning material. Wear can be suppressed.
以下、この発明の実施形態に係るクラッチレリーズ軸受装置Aを添付図面に基づいて説明する。なお、以下の説明では、図5において、紙面右側を軸方向一方側(トランスミッション側)、紙面左側を軸方向他方側(エンジン側)と呼ぶことがある。
Hereinafter, a clutch release bearing device A according to an embodiment of the present invention will be described with reference to the accompanying drawings. In the following description, in FIG. 5, the right side of the drawing may be referred to as one axial side (transmission side), and the left side of the drawing may be referred to as the other axial side (engine side).
クラッチレリーズ軸受装置Aは、図5に示すように、トランスミッションのインプットシャフト38が貫通するクラッチケース36のフロントカバー34の外周に、軸方向にスライド自在に取り付けられており、レリーズフォーク32の揺動に伴ってフロントカバー34上を軸方向他方側(エンジン側)に向かって軸方向にスライドし、クラッチ装置Bのダイヤフラムスプリング40を押し付けて、これにより、ダイヤフラムスプリング40が撓み、プレッシャプレート42がクラッチディスク44から離れて、クラッチが切れ、エンジンの出力軸50からの動力を遮断した状態にする。
As shown in FIG. 5, the clutch release bearing device A is attached to the outer periphery of the front cover 34 of the clutch case 36 through which the input shaft 38 of the transmission penetrates so as to be slidable in the axial direction. As a result, the front cover 34 is slid in the axial direction toward the other side (engine side) in the axial direction and the diaphragm spring 40 of the clutch device B is pressed, whereby the diaphragm spring 40 is bent and the pressure plate 42 is clutched. The clutch is disengaged away from the disk 44, and the power from the engine output shaft 50 is cut off.
この発明の実施形態に係るクラッチレリーズ軸受装置Aは、図1に示すように、スリーブ1と、このスリーブ1に外嵌されたレリーズ軸受2と、クラッチレリーズフォーク32(図5参照)が当接する略円板状の側板3と、レリーズ軸受2に所定の軸方向荷重を付与する弾性部材4と、スリーブ1、レリーズ軸受2、側板3及び弾性部材4を保持するカバー5とを備えている。
In the clutch release bearing device A according to the embodiment of the present invention, as shown in FIG. 1, a sleeve 1, a release bearing 2 fitted on the sleeve 1, and a clutch release fork 32 (see FIG. 5) abut. A substantially disc-shaped side plate 3, an elastic member 4 that applies a predetermined axial load to the release bearing 2, and a sleeve 1, the release bearing 2, the side plate 3, and a cover 5 that holds the elastic member 4 are provided.
この実施形態に係るクラッチレリーズ軸受装置Aは、後述するように、エンジン側の軸心とトランスミッション側の軸心との間にずれが生じた場合、レリーズ軸受2をずれ量に応じて径方向に摺動させることで、両軸心間の心ずれを自動的に調心する、自動調心型である。
As will be described later, the clutch release bearing device A according to this embodiment causes the release bearing 2 to move in the radial direction according to the amount of displacement when a displacement occurs between the engine-side shaft center and the transmission-side shaft center. It is a self-aligning type that automatically aligns the misalignment between the two axes by sliding.
スリーブ1は、トランスミッションのクラッチカバー36に突設されたフロントカバー34上を軸方向に摺動可能なスリーブであり、円筒状である。スリーブ1は、樹脂製であり、例えば、PA(ポリアミド)66等の熱可塑性合成樹脂である。スリーブ1を形成する樹脂材料には、カーボンファイバー等の強化材を5~25wt%添加してもよい。
The sleeve 1 is a sleeve that is slidable in the axial direction on the front cover 34 protruding from the clutch cover 36 of the transmission, and has a cylindrical shape. The sleeve 1 is made of a resin, for example, a thermoplastic synthetic resin such as PA (polyamide) 66. The resin material forming the sleeve 1 may contain 5 to 25 wt% of a reinforcing material such as carbon fiber.
レリーズ軸受2は、外輪6と、内輪7と、保持器8と、転動体9とからなる。レリーズ軸受2は、スリーブ1に所定の径方向隙間S1を介して外嵌されている。外輪6には、内周に外側軌道面6aを有している。内輪7は、外輪6の内径側に設けられ、外周に外側軌道面6aに対向する内側軌道面7aを有している。内輪7は、円筒状である。内輪7には、ダイヤフラムスプリング40側の軸方向端部に、外輪6の軸方向端面(保護カバー5)より軸方向外側に延長された延長部7bが形成されている。
The release bearing 2 includes an outer ring 6, an inner ring 7, a cage 8, and rolling elements 9. The release bearing 2 is externally fitted to the sleeve 1 via a predetermined radial gap S1. The outer ring 6 has an outer raceway surface 6a on the inner periphery. The inner ring 7 is provided on the inner diameter side of the outer ring 6, and has an inner raceway surface 7a facing the outer raceway surface 6a on the outer periphery. The inner ring 7 is cylindrical. The inner ring 7 is formed with an extended portion 7 b that extends outward in the axial direction from the axial end surface (protective cover 5) of the outer ring 6 at the axial end on the diaphragm spring 40 side.
このように、内輪7は、内輪軌道面7aを有して外輪6と略同一の軸方向寸法を有する本体部と、当該本体部(外輪6の軸方向他方側端面)よりも軸方向他方側に延長した延長部(軸方向他方側(エンジン側)に突出した突出部)とで構成されている。外輪6の外側軌道面6aと内輪7の内側軌道面7aとの間には、保持器8を介して複数の転動体(ボール)9が転動自在に収容されている。外輪6の両端部にはシール10、11が装着されている。シール10、11は、軸受内部に封入された潤滑グリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。
As described above, the inner ring 7 has the inner ring raceway surface 7a and the main body portion having substantially the same axial dimension as the outer ring 6, and the other axial end side of the main body portion (the other axial end surface of the outer ring 6). And an extended portion (a protruding portion protruding to the other side in the axial direction (engine side)). Between the outer raceway surface 6 a of the outer ring 6 and the inner raceway surface 7 a of the inner ring 7, a plurality of rolling elements (balls) 9 are accommodated via a cage 8 so as to be able to roll. Seals 10 and 11 are attached to both ends of the outer ring 6. The seals 10 and 11 prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater and dust from the outside into the bearing.
内輪7は、スリーブ1に外挿されており、クラッチペダル(図示省略)を踏むと、ダイヤフラムスプリング40側に向かって軸方向に延びる延長部7bが、フロントカバー34を囲むように放射状に設けられたダイヤフラムスプリング40のスプリング歯40bを後述する緩衝材31を介して軸方向に押し付けて、ダイヤフラムスプリング40の撓みによって、プレッシャプレート42がクラッチディスク44から離れ、エンジンの出力軸50からの動力がトランスミッションから一時的に切り離される。本実施形態では、内輪7がダイヤフラムスプリング40を押し付ける押付部材である。なお、押付部材は、外輪であってもよいし、内輪内径に圧入される別部材であってもよい。
The inner ring 7 is externally attached to the sleeve 1, and when a clutch pedal (not shown) is stepped on, an extension portion 7 b extending in the axial direction toward the diaphragm spring 40 side is provided radially so as to surround the front cover 34. The spring teeth 40b of the diaphragm spring 40 are pressed in the axial direction via a cushioning material 31 to be described later, the pressure plate 42 is separated from the clutch disk 44 by the bending of the diaphragm spring 40, and the power from the engine output shaft 50 is transmitted to the transmission. Temporarily disconnected from. In the present embodiment, the inner ring 7 is a pressing member that presses the diaphragm spring 40. The pressing member may be an outer ring or may be a separate member that is press-fitted into the inner ring inner diameter.
ダイヤフラムスプリング40は、プレッシャプレート42とクラッチカバー45との間に配置された円板状の部材である。ダイヤフラムスプリング40は、プレッシャプレート42に当接する環状の円形基部40aと、当該円形基部40aの内周部から径方向内側に延びるスプリング歯40bとを有している。円形基部40aは、プレッシャプレート42をフライホイール33側に当接している。スプリング歯40b間はスリットになっている。クラッチ遮断時、スプリング歯40bの先端が緩衝材31を介してレリーズ軸受2の内輪7によって押し付けられて軸方向(フライホイール側)に移動することで、プレッシャプレート42への付勢力が解除される。
The diaphragm spring 40 is a disk-shaped member disposed between the pressure plate 42 and the clutch cover 45. The diaphragm spring 40 has an annular circular base portion 40a that contacts the pressure plate 42, and spring teeth 40b that extend radially inward from the inner peripheral portion of the circular base portion 40a. The circular base 40a abuts the pressure plate 42 on the flywheel 33 side. A slit is formed between the spring teeth 40b. When the clutch is disengaged, the tip of the spring tooth 40b is pressed by the inner ring 7 of the release bearing 2 through the cushioning material 31 and moves in the axial direction (flywheel side), so that the urging force on the pressure plate 42 is released. .
側板3は、図4に示すように、略円板であり、鋼鈑素材をプレス加工することで形成されている。側板3は、鋼板素材として、浸炭鋼板を用いている。この実施形態では、側板3を形成する鋼板の素材は、SCM(クロムモリブデン鋼)である。SCMからなる冷間圧延鋼板をプレス加工することにより、所定形状に形成されている。
As shown in FIG. 4, the side plate 3 is a substantially circular plate and is formed by pressing a steel plate material. The side plate 3 uses a carburized steel plate as a steel plate material. In this embodiment, the material of the steel plate forming the side plate 3 is SCM (chromium molybdenum steel). The cold-rolled steel sheet made of SCM is formed into a predetermined shape by pressing.
側板3は、インサート成形により樹脂製のスリーブ1と一体化されている。側板3には、クラッチレリーズフォーク32に係合してそれをガイドする本体部3aが形成されている。
The side plate 3 is integrated with the resin sleeve 1 by insert molding. The side plate 3 is formed with a main body portion 3a that engages with and guides the clutch release fork 32.
側板3は、本体部3aの内径縁から軸方向一方側(トランスミッション側)に延びる鍔部3cを有する。鍔部3cは、スリーブ1に埋設されている。本体部3aの一部と鍔部3cとによって、スリーブ1に埋設される内径部3bが構成される。鍔部3cには、スリーブ1に対する側板3の回り止め機能を有する切欠き部3dが設けられている。
The side plate 3 has a flange 3c that extends from the inner diameter edge of the main body 3a to one side in the axial direction (transmission side). The collar portion 3 c is embedded in the sleeve 1. An inner diameter portion 3b embedded in the sleeve 1 is constituted by a part of the main body portion 3a and the flange portion 3c. The collar portion 3c is provided with a notch portion 3d having a function of preventing the side plate 3 from rotating with respect to the sleeve 1.
なお、鍔部3cは、本体部3aの内径縁から軸方向他方側(エンジン側)に延びていてもよい。
The flange portion 3c may extend from the inner diameter edge of the main body portion 3a to the other side in the axial direction (engine side).
弾性部材4は、例えば、鋼板プレス成型品の皿バネである。具体的には、弾性部材4は、複数、例えば3~5個の波を有する断面が平坦な有端リングからなり、鋼線(JIS規格のSW、SWP系)等の線材から波押しおよび丸め成形され、熱処理により歪み取り焼鈍後、時効硬化処理が施されている。
The elastic member 4 is, for example, a disc spring of a steel plate press-formed product. Specifically, the elastic member 4 is composed of a plurality of end rings having a flat cross section, for example, 3 to 5 waves, and corrugated and rounded from a wire such as a steel wire (JIS standard SW, SWP system). After being molded and subjected to strain relief annealing by heat treatment, age hardening treatment is performed.
カバー5は、耐食性を有する鋼板、例えば、冷間圧延鋼鈑(JIS規格のSPCC系)やオーステナイト系ステンレス鋼板(JIS規格のSUS304系)等をプレス加工にて前記レリーズ軸受2を覆う円筒状に形成されている。カバー5は、一端部に弾性部材4を収容する内フランジ5aが形成されると共に、他端部に周方向複数箇所に舌片5bが形成されている。この舌片5bが側板3の外径部に加締められ、弾性部材4、外輪6、および側板3が分離しないように保持している。
The cover 5 is formed in a cylindrical shape that covers the release bearing 2 by pressing a steel plate having corrosion resistance, for example, a cold rolled steel plate (JIS standard SPCC system) or an austenitic stainless steel sheet (JIS standard SUS304 system). Is formed. The cover 5 has an inner flange 5a for accommodating the elastic member 4 at one end, and tongues 5b at a plurality of locations in the circumferential direction at the other end. The tongue piece 5b is crimped to the outer diameter portion of the side plate 3 and is held so that the elastic member 4, the outer ring 6, and the side plate 3 are not separated.
弾性部材4は、カバー5の内フランジ5aとの間で摺動することがないため、カバー5に偏摩耗が生じることはない。したがって、所定の保持力を維持し、調心位置にレリーズ軸受2を長期間安定して保持することができる。
Since the elastic member 4 does not slide between the inner flange 5a of the cover 5, the cover 5 will not be unevenly worn. Therefore, a predetermined holding force can be maintained and the release bearing 2 can be stably held at the alignment position for a long period of time.
即ち、レリーズ軸受2の外輪6は、複数の波を有する有端リングからなる弾性部材4によって弾性的に保持され、かつ、レリーズ軸受2はスリーブ1に所定の径方向隙間を介して外嵌されている。
That is, the outer ring 6 of the release bearing 2 is elastically held by the elastic member 4 formed of a ring having a plurality of waves, and the release bearing 2 is fitted on the sleeve 1 via a predetermined radial gap. ing.
スリーブ1の外周とレリーズ軸受2の内輪7の内周との間には、半径方向すきまS1が設けられており、レリーズ軸受2の外輪6の外周とカバー5の内周との間には、当該半径方向すきまS1よりも小さい半径方向すきまS2が設けられている。そして、外輪6とカバー5の内側面との間に介在される弾性部材4の付勢力によって、外輪6が側板3の端面に弾性的に押圧される。これにより、レリーズ軸受2がスリーブ1の外周と側板3の端面との間において半径方向摺動自在すなわちフローティング可能に弾性保持される。レリーズ軸受2は、半径方向すきまS1,S2によって、スリーブ1および側板3に対して半径方向に調心移動が可能であり、その調心移動量は小さい方の半径方向すきまS2によって規制される。よって、スリーブ1の軸心と出力軸50の軸心との間に組み込み上の誤差等があり、ダイヤフラムスプリング40の回転中心とクラッチレリーズ軸受装置Aの回転中心とで心ずれが生じても、レリーズ軸受2がそのずれ量に応じて調心移動することによって、心ずれが自動的に調心される。
A radial clearance S1 is provided between the outer periphery of the sleeve 1 and the inner periphery of the inner ring 7 of the release bearing 2, and between the outer periphery of the outer ring 6 of the release bearing 2 and the inner periphery of the cover 5, A radial clearance S2 smaller than the radial clearance S1 is provided. The outer ring 6 is elastically pressed against the end surface of the side plate 3 by the biasing force of the elastic member 4 interposed between the outer ring 6 and the inner side surface of the cover 5. Thereby, the release bearing 2 is elastically held between the outer periphery of the sleeve 1 and the end face of the side plate 3 so as to be slidable in the radial direction, that is, floatable. The release bearing 2 can be aligned in the radial direction with respect to the sleeve 1 and the side plate 3 by the radial clearances S1 and S2, and the alignment movement amount is regulated by the smaller radial clearance S2. Therefore, there is an error in assembling between the shaft center of the sleeve 1 and the shaft center of the output shaft 50, and even if a center shift occurs between the rotation center of the diaphragm spring 40 and the rotation center of the clutch release bearing device A, When the release bearing 2 moves in alignment according to the amount of deviation, the center deviation is automatically adjusted.
次に、図2及び3を参照しながら、この発明の自動調心型のクラッチレリーズ軸受装置Aにおいては、レリーズ軸受2の内輪7のダイヤフラムスプリング40側の軸方向端部に設けられた延長部7bとダイヤフラムスプリング40のスプリング歯40bとの間に環状の緩衝材31が設けられている。
Next, referring to FIGS. 2 and 3, in the self-aligning clutch release bearing device A of the present invention, the extension provided at the axial end of the inner ring 7 of the release bearing 2 on the diaphragm spring 40 side. An annular cushioning material 31 is provided between 7 b and the spring teeth 40 b of the diaphragm spring 40.
緩衝材31は、ポリアミド樹脂からなる樹脂材であり、内輪7の延長部7bに加硫接着することで取り付けられている。緩衝材31はダイヤフラム40に接触する環状部31aと、後述する延長部7bの凹部7cに係合する凸部31bとを有している。緩衝材31の内径は内輪7の内径よりも小さいことで、凸部31bの厚みは環状部31aの厚みと同等になり、緩衝材31を延長部7bに加硫接着し易くなる。
The buffer material 31 is a resin material made of polyamide resin, and is attached to the extension portion 7b of the inner ring 7 by vulcanization adhesion. The cushioning material 31 has an annular portion 31a that contacts the diaphragm 40, and a convex portion 31b that engages with a concave portion 7c of an extension portion 7b described later. Since the inner diameter of the cushioning material 31 is smaller than the inner diameter of the inner ring 7, the thickness of the convex portion 31b becomes equal to the thickness of the annular portion 31a, and the cushioning material 31 is easily vulcanized and bonded to the extension portion 7b.
クラッチディスク44がフライホイール33に当接してクラッチが連結しているとき(ダイヤフラムスプリング40をレリーズ軸受2が押し付けていないとき)、緩衝材31と内輪7の延長部7bとの間に軸方向の隙間S3が設けられている。隙間S3は、複数のスプリング歯40bのうちダイヤフラムスプリング40(の円形基部40a)の外周縁に対して最も離れた位置にあるスプリング歯40b1の当該外周縁に対する軸方向高さLmaxと、円形基部40aの外周縁に対して最も近い位置にあるスプリング歯40b2の当該外周縁に対する軸方向高さLminとの差よりも大きい。なお、本願明細書では、図2及び6を参照の通り、円形基部40aの外周縁を通って軸方向に直交する方向に延びる仮想線Vからスプリング歯40b1,40b2の先端縁までの距離を「スプリング歯40bの軸方向高さ」と定義している。クラッチディスク44がフライホイール33から離れてクラッチが遮断されたとき、緩衝材31と内輪7の延長部7bとの間の軸方向の隙間は、クラッチが連結しているときの隙間S3よりも小さくなる。すなわち、レリーズ軸受2がダイヤフラムスプリング40を押し付けてクラッチが遮断されたときは、緩衝材31と延長部7bとの間に軸方向の隙間は、スプリング歯40bの軸方向高さの寸法差を吸収する分だけ隙間S3よりも小さくなる。緩衝材31がダイヤフラムスプリング40を押し付ける内輪7に取り付けられていることで、簡易かつコンパクトな構造で緩衝材31の摩耗を防止することができる。なお、緩衝材31は、ダイヤフラムスプリング40側に取り付けるようにしてもよい。
When the clutch disc 44 is in contact with the flywheel 33 and the clutch is engaged (when the diaphragm spring 40 is not pressed against the release bearing 2), the axial direction between the cushioning material 31 and the extension 7b of the inner ring 7 is maintained. A gap S3 is provided. The gap S3 includes an axial height Lmax of the spring tooth 40b1 that is farthest from the outer peripheral edge of the diaphragm spring 40 (the circular base part 40a) of the plurality of spring teeth 40b, and the circular base part 40a. This is larger than the difference between the spring tooth 40b2 located closest to the outer peripheral edge and the axial height Lmin relative to the outer peripheral edge. In this specification, as shown in FIGS. 2 and 6, the distance from the imaginary line V extending in the direction orthogonal to the axial direction through the outer peripheral edge of the circular base 40a to the tip edges of the spring teeth 40b1 and 40b2 is expressed as “ It is defined as "the axial height of the spring teeth 40b". When the clutch disc 44 is separated from the flywheel 33 and the clutch is disengaged, the axial clearance between the cushioning material 31 and the extension 7b of the inner ring 7 is smaller than the clearance S3 when the clutch is engaged. Become. That is, when the release bearing 2 presses the diaphragm spring 40 and the clutch is disengaged, the axial gap between the cushioning material 31 and the extension 7b absorbs the dimensional difference in the axial height of the spring teeth 40b. Therefore, it becomes smaller than the gap S3. Since the cushioning material 31 is attached to the inner ring 7 that presses the diaphragm spring 40, wear of the cushioning material 31 can be prevented with a simple and compact structure. The buffer material 31 may be attached to the diaphragm spring 40 side.
このように、クラッチが連結しているときにレリーズ軸受2の内輪7の延長部7bと緩衝材31との間に隙間S3を設けることで、各スプリング歯40bの軸方向の高さに寸法差が生じていても、クラッチをレリーズするためにダイヤフラムスプリング40をレリーズ軸受2が押し付けたときに、その寸法差を隙間S3によって吸収して、緩衝材31が延長部7bの軸方向端面に対して均一に荷重を付加する。これにより、緩衝材31に大きな面圧が生じにくくなるので、緩衝材31の摩耗を抑制することができる。また、クラッチが連結しているときには、緩衝材31と内輪7との間に隙間S3が設けられていることで、振動による緩衝材31の摩耗を抑制することができる。ここで、クラッチが連結しているときに緩衝材31と内輪7との間に隙間S3が設けられていると、緩衝材31が内輪7に対して周方向に回転する可能性がある。緩衝材31の内輪7に対する回転(滑り)を防止するために、内輪7の延長部7bに回り止め用の凹部7cが設けられている。凹部7cは、延長部7bの内周面の一部を外径側に凹ませることでなる。緩衝材31の環状部31aのうち内輪7と軸方向に対向する面の内径側部分から突出する凸部31bが凹部7cと係合することで、緩衝材31が回り止めされる。本実施形態では、内輪7に複数の凹部7cが設けられており、中心Oを挟んで互いに対向するように設けられている。なお、緩衝材31に設けた凹部に延長部7bに設けた凸部を係合してもよいし、緩衝材31と延長部7bそれぞれに凹部と凸部両方を設けて、相手部材と互いに係合するようにしてもよい。
Thus, by providing the clearance S3 between the extension portion 7b of the inner ring 7 of the release bearing 2 and the cushioning material 31 when the clutch is engaged, there is a dimensional difference in the axial height of each spring tooth 40b. When the release bearing 2 presses the diaphragm spring 40 to release the clutch, the dimensional difference is absorbed by the gap S3, so that the cushioning material 31 is against the axial end surface of the extension 7b. Apply a uniform load. Thereby, since it becomes difficult to produce a big surface pressure in the shock absorbing material 31, abrasion of the shock absorbing material 31 can be suppressed. Further, when the clutch is engaged, the clearance S3 is provided between the buffer material 31 and the inner ring 7, so that wear of the buffer material 31 due to vibration can be suppressed. Here, if the clearance S <b> 3 is provided between the buffer material 31 and the inner ring 7 when the clutch is engaged, the buffer material 31 may rotate in the circumferential direction with respect to the inner ring 7. In order to prevent the cushioning material 31 from rotating (sliding) with respect to the inner ring 7, the extension part 7 b of the inner ring 7 is provided with a recess 7 c for preventing rotation. The recess 7c is formed by denting a part of the inner peripheral surface of the extension 7b to the outer diameter side. The projection 31b protruding from the inner diameter side portion of the annular portion 31a of the cushioning material 31 facing the inner ring 7 in the axial direction engages with the depression 7c, so that the cushioning material 31 is prevented from rotating. In the present embodiment, the inner ring 7 is provided with a plurality of recesses 7c so as to face each other across the center O. In addition, the convex part provided in the extension part 7b may be engaged with the concave part provided in the buffer material 31, or both the concave part and the convex part are provided in the buffer material 31 and the extension part 7b, respectively. You may make it match.
図9に基づく参考例は、以下に付記する発明を開示する。
図9に示すクラッチレリーズ軸受装置は、周方向に複数のスプリング歯40bを有するダイヤフラムスプリング40を軸方向に押し付けるレリーズ軸受2Aを有し、当該レリーズ軸受2Aの内輪7に設けられた延長部7Abとダイヤフラムスプリング40との間に緩衝材31Aを設けたクラッチレリーズ軸受装置において、緩衝材31Aをゴム材としたことを特徴とする。 The reference example based on FIG. 9 discloses the invention appended below.
The clutch release bearing device shown in FIG. 9 has arelease bearing 2A that presses a diaphragm spring 40 having a plurality of spring teeth 40b in the circumferential direction in the axial direction, and an extension 7Ab provided on the inner ring 7 of the release bearing 2A. In the clutch release bearing device in which the buffer material 31A is provided between the diaphragm spring 40 and the diaphragm spring 40, the buffer material 31A is a rubber material.
図9に示すクラッチレリーズ軸受装置は、周方向に複数のスプリング歯40bを有するダイヤフラムスプリング40を軸方向に押し付けるレリーズ軸受2Aを有し、当該レリーズ軸受2Aの内輪7に設けられた延長部7Abとダイヤフラムスプリング40との間に緩衝材31Aを設けたクラッチレリーズ軸受装置において、緩衝材31Aをゴム材としたことを特徴とする。 The reference example based on FIG. 9 discloses the invention appended below.
The clutch release bearing device shown in FIG. 9 has a
図9に示すクラッチレリーズ軸受装置では、ダイヤフラムスプリング40と内輪7との間に別体の緩衝材31Aが設けられている。緩衝材31Aはリング状であり、緩衝材31Aは、内輪7の延長部7Abに加硫接着されている。緩衝材31Aは、例えば、ニトリルゴム(NBR)、アクリルゴム(ACM)、フッ化ビニリデン系ゴム(FKM)などのゴム材である。
In the clutch release bearing device shown in FIG. 9, a separate cushioning material 31 </ b> A is provided between the diaphragm spring 40 and the inner ring 7. The buffer material 31 </ b> A has a ring shape, and the buffer material 31 </ b> A is vulcanized and bonded to the extension 7 </ b> Ab of the inner ring 7. The buffer material 31A is, for example, a rubber material such as nitrile rubber (NBR), acrylic rubber (ACM), or vinylidene fluoride rubber (FKM).
図9に示すクラッチレリーズ軸受装置では、ダイヤフラムスプリング40とレリーズ軸受2Aの延長部7Abとの間にゴム材である緩衝材31が挟み込まれるので、ダイヤフラムスプリング40のスプリング歯40bの周方向の高さバラつきをゴム材31が吸収し、レリーズ軸受2Aの延長部7Abに均一に荷重が負荷されるため、振動の発生を抑制することができる。また、ゴム材31の摩擦力によって、周方向に滑り難くできるため、ダイヤフラムスプリング40とレリーズ軸受2Aのコンタクト面7Abの摩耗を抑制できる。さらに、一般的にスプリング歯40b及びレリーズ軸受2Aの延長部7Abは互い周方向に線接触となるように一方を線、もう他方を弧として設計するが、緩衝材31Aをゴム材とすることで、双方の形状に沿って変形するため、形状にとらわれない設計とすることもできる。
In the clutch release bearing device shown in FIG. 9, since the cushioning material 31 that is a rubber material is sandwiched between the diaphragm spring 40 and the extension portion 7Ab of the release bearing 2A, the circumferential height of the spring teeth 40b of the diaphragm spring 40 Since the rubber material 31 absorbs the variation and the load is uniformly applied to the extension portion 7Ab of the release bearing 2A, the occurrence of vibration can be suppressed. Further, since the frictional force of the rubber material 31 makes it difficult to slip in the circumferential direction, wear of the diaphragm spring 40 and the contact surface 7Ab of the release bearing 2A can be suppressed. Furthermore, generally, the spring teeth 40b and the extension portion 7Ab of the release bearing 2A are designed so that one is a line and the other is an arc so as to be in line contact with each other in the circumferential direction. Since it deforms along both shapes, the design can be made independent of the shape.
以上、この発明の実施の形態について説明を行ったが、この発明はこうした実施の形態に何等限定されるものではなく、あくまで例示であって、この発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得る。
The embodiment of the present invention has been described above. However, the present invention is not limited to such an embodiment, and is merely an example. Various modifications can be made without departing from the scope of the present invention. Can be implemented.
1 :スリーブ
2 :レリーズ軸受
6 :外輪
7 :内輪
7b :延長部
31 :緩衝材
40 :ダイヤフラムスプリング
40b :スプリング歯
A :自動調心型クラッチレリーズ軸受装置
B :クラッチ装置
S3 :隙間 1: Sleeve 2: Release bearing 6: Outer ring 7:Inner ring 7b: Extension part 31: Buffer material 40: Diaphragm spring 40b: Spring tooth A: Self-aligning clutch release bearing device B: Clutch device S3: Clearance
2 :レリーズ軸受
6 :外輪
7 :内輪
7b :延長部
31 :緩衝材
40 :ダイヤフラムスプリング
40b :スプリング歯
A :自動調心型クラッチレリーズ軸受装置
B :クラッチ装置
S3 :隙間 1: Sleeve 2: Release bearing 6: Outer ring 7:
Claims (4)
- 周方向に複数のスプリング歯を有するダイヤフラムスプリングを樹脂製の緩衝材を介して押し付けるレリーズ軸受を備えたクラッチレリーズ軸受装置において、前記ダイヤフラムスプリングを前記レリーズ軸受が押し付けていないとき、前記緩衝材と前記レリーズ軸受との間に隙間が設けられていることを特徴とするクラッチレリーズ軸受装置。 In a clutch release bearing device provided with a release bearing that presses a diaphragm spring having a plurality of spring teeth in the circumferential direction through a resin cushioning material, when the diaphragm bearing is not pressed against the diaphragm spring, the cushioning material and the A clutch release bearing device, wherein a gap is provided between the release bearing and the release bearing.
- 前記緩衝材が、前記レリーズ軸受のうち前記ダイヤフラムスプリングを押し付ける押付部材に取り付けられている請求項1記載のクラッチレリーズ軸受装置。 The clutch release bearing device according to claim 1, wherein the cushioning material is attached to a pressing member that presses the diaphragm spring of the release bearing.
- 前記緩衝材が、前記レリーズ軸受に対し周方向に回り止めされている請求項1又は2に記載のクラッチレリーズ軸受装置。 The clutch release bearing device according to claim 1 or 2, wherein the cushioning material is prevented from rotating in a circumferential direction with respect to the release bearing.
- 前記複数のスプリング歯のうち前記ダイヤフラムスプリングの外周縁に対して最も離れた位置にあるスプリング歯の当該外周縁に対する軸方向高さと、前記外周縁に対して最も近い位置にあるスプリング歯の当該外周縁に対する軸方向高さとの差よりも前記隙間を大きくしたことを特徴とする請求項1~3のいずれかに記載のクラッチレリーズ軸受装置。 Of the plurality of spring teeth, the axial height of the spring tooth that is farthest from the outer peripheral edge of the diaphragm spring with respect to the outer peripheral edge and the outer periphery of the spring tooth that is closest to the outer peripheral edge The clutch release bearing device according to any one of claims 1 to 3, wherein the gap is made larger than a difference between the height in the axial direction relative to a peripheral edge.
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JP2018039220A JP6923468B2 (en) | 2018-03-06 | 2018-03-06 | Clutch release bearing device |
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JPS51137045U (en) * | 1975-04-25 | 1976-11-05 | ||
JPS52118861U (en) * | 1976-03-05 | 1977-09-09 | ||
JPS57149627A (en) * | 1981-02-11 | 1982-09-16 | Valeo | Clutch releasing bearing |
US4555190A (en) * | 1985-01-17 | 1985-11-26 | General Motors Corporation | Clutch release bearing assembly |
JPH0581537U (en) * | 1992-04-06 | 1993-11-05 | 株式会社大金製作所 | Clutch cover assembly |
JPH0710565U (en) * | 1993-07-27 | 1995-02-14 | 光洋精工株式会社 | Clutch release bearing |
US20030226735A1 (en) * | 2002-06-07 | 2003-12-11 | Zf Sachs Ag | Clutch release mechanism for compensating for misalignments in a friction clutch of a motor vehicle |
JP2012013199A (en) * | 2010-07-05 | 2012-01-19 | Jtekt Corp | Clutch release bearing device |
-
2018
- 2018-03-06 JP JP2018039220A patent/JP6923468B2/en active Active
-
2019
- 2019-03-01 WO PCT/JP2019/008111 patent/WO2019172122A1/en active Application Filing
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JPS51137045U (en) * | 1975-04-25 | 1976-11-05 | ||
JPS52118861U (en) * | 1976-03-05 | 1977-09-09 | ||
JPS57149627A (en) * | 1981-02-11 | 1982-09-16 | Valeo | Clutch releasing bearing |
US4555190A (en) * | 1985-01-17 | 1985-11-26 | General Motors Corporation | Clutch release bearing assembly |
JPH0581537U (en) * | 1992-04-06 | 1993-11-05 | 株式会社大金製作所 | Clutch cover assembly |
JPH0710565U (en) * | 1993-07-27 | 1995-02-14 | 光洋精工株式会社 | Clutch release bearing |
US20030226735A1 (en) * | 2002-06-07 | 2003-12-11 | Zf Sachs Ag | Clutch release mechanism for compensating for misalignments in a friction clutch of a motor vehicle |
JP2012013199A (en) * | 2010-07-05 | 2012-01-19 | Jtekt Corp | Clutch release bearing device |
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JP2019152297A (en) | 2019-09-12 |
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