WO2011045987A1 - クラッチカバー組立体 - Google Patents
クラッチカバー組立体 Download PDFInfo
- Publication number
- WO2011045987A1 WO2011045987A1 PCT/JP2010/065109 JP2010065109W WO2011045987A1 WO 2011045987 A1 WO2011045987 A1 WO 2011045987A1 JP 2010065109 W JP2010065109 W JP 2010065109W WO 2011045987 A1 WO2011045987 A1 WO 2011045987A1
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- WIPO (PCT)
- Prior art keywords
- clutch cover
- diaphragm spring
- flywheel
- pressure plate
- clutch
- Prior art date
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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
- F16D13/583—Diaphragm-springs, e.g. Belleville
- F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate
Definitions
- the present invention relates to a clutch cover assembly, and more particularly, to press and release a friction member of a clutch disassembly against a flywheel of an engine.
- the clutch cover assembly is generally mounted on an engine flywheel and used to transmit engine driving force to the transmission side.
- a clutch cover assembly mainly includes a clutch cover fixed to the flywheel, a pressure plate for sandwiching the friction member of the clutch disk assembly between the flywheel, and the pressure plate on the flywheel side. It is comprised from the diaphragm spring for pressing.
- the diaphragm spring includes an annular elastic portion and a plurality of lever portions extending radially inward from the inner peripheral edge of the annular elastic portion.
- the diaphragm spring has a function of pressing the pressure plate and a lever function for releasing the pressure on the pressure plate.
- the diaphragm spring is supported on the clutch cover by a plurality of tabs formed by bending a part of the inner peripheral portion of the clutch cover (see Patent Document 1).
- the clutch cover has a high rigidity.
- the clutch cover is formed by pressing a sheet metal, it is conceivable to increase the thickness of the clutch cover in order to increase the rigidity of the clutch cover.
- increasing the thickness of the clutch cover is not preferable because the weight increases.
- An object of the present invention is to provide a clutch cover assembly of a type in which a tab is formed by using a part of the clutch cover and a diaphragm spring is supported by the tab. Is to prevent it from getting worse.
- the clutch cover assembly according to the first invention is for pressing and releasing the friction member of the clutch disk assembly against the flywheel of the engine, and includes a clutch cover, a pressure plate, and a diaphragm spring.
- the clutch cover can be fixed to the flywheel, has a circular opening in the center, and is folded between the inner peripheral portion and the outer peripheral portion on the flywheel side and is bent on the outer peripheral side. It has a tab and the inner peripheral edge portion is continuous in an annular shape.
- the pressure plate is connected to the clutch cover so as not to rotate relative to the clutch cover, and sandwiches the friction member with the flywheel.
- the diaphragm spring is supported by a plurality of tabs of the clutch cover and urges the pressure plate toward the flywheel.
- the clutch cover of the present invention has higher rigidity than the conventional clutch cover, is not easily deformed even when the release force is applied, and has a small amount of deflection. Therefore, the clutch disengagement performance is improved.
- the clutch cover assembly according to a second aspect of the present invention is the clutch cover assembly according to the first aspect of the invention, wherein an inner peripheral edge of the clutch cover is formed with a flange that protrudes away from the flywheel in the axial direction and continues in an annular shape. Yes.
- the flange portion is formed on the inner peripheral edge portion of the clutch cover, the rigidity of the clutch cover becomes higher. Accordingly, the amount of deflection of the clutch cover during the release operation is further reduced, and the clutch disengagement performance is further improved.
- a clutch cover assembly is the clutch cover assembly of the first aspect, further comprising a pair of wirings that support the diaphragm spring together with a plurality of tabs.
- a clutch cover assembly according to a fourth invention is the clutch cover assembly according to the first invention, wherein the clutch cover is formed with a plurality of holes for forming a plurality of tabs, and the plurality of holes are respectively It forms independently of the adjacent punch hole, and the bridge part which connects an outer peripheral part and an inner peripheral part is formed between the adjacent punch holes.
- the bridge portion is formed between the plurality of holes for forming the tab, the rigidity of the clutch cover becomes higher and the clutch disengagement performance is further improved.
- a clutch cover assembly is the clutch cover assembly according to the first aspect, wherein at least one elastic member that is supported by the clutch cover and generates a load that opposes the biasing force of the diaphragm spring, and a flywheel of a pressure plate And a limiting mechanism that limits the movement to the side within a certain range.
- the clutch cover includes a fixed portion fixed to the flywheel, and a portion disposed on the radially inner side of the fixed portion.
- the clutch cover has at least one storage portion that is recessed toward the pressure plate and stores the elastic member. ing.
- the limiting mechanism is realized by the diaphragm spring coming into contact with the clutch cover.
- the elastic member is disposed on the opposite side to the pressure plate of the diaphragm spring in the axial direction.
- the maximum allowable wear amount of the friction member means the maximum wear amount in a range in which the friction member can exhibit a desired torque transmission characteristic.
- the clutch cover assembly according to a sixth aspect of the present invention is the clutch cover assembly according to the fifth aspect of the present invention, wherein the limiting mechanism is realized by a diaphragm spring coming into contact with the accommodating portion.
- the clutch cover assembly according to a seventh aspect of the present invention is the clutch cover assembly according to the fifth aspect, wherein the limiting mechanism is realized by a diaphragm spring coming into contact with the inner peripheral end of the clutch cover.
- the clutch cover assembly according to an eighth aspect of the present invention is the clutch cover assembly of the fifth aspect, wherein the axial position of the pressure plate restricted by the restriction mechanism is in a state where the wear amount of the friction member has reached the maximum allowable wear amount. Corresponds to the pressing position of the pressure plate.
- FIG. 2 is a schematic plan view of the clutch cover assembly.
- FIG. 3 is a partially enlarged view of FIG. 2. The figure for demonstrating the pressing load characteristic.
- FIG. 1 is a schematic longitudinal sectional view of the clutch cover assembly 1
- FIG. 2 is a schematic plan view of the clutch cover assembly 1.
- the OO line shown in the figure is the rotational axis of the flywheel 51 and the clutch cover assembly 1.
- the left side of the figure is referred to as the axial engine side
- the right side of the figure is referred to as the axial transmission side.
- the clutch cover assembly 1 is configured to press the friction member 53 of the clutch disc assembly 52 against the flywheel 51 of the engine to connect (turn on) the clutch, release the pressure, and disconnect (turn off) the clutch.
- the friction member 53 includes a friction facing and a cushioning plate, and has a cushioning function that can bend in a predetermined range in the axial direction.
- the clutch cover assembly 1 mainly includes a clutch cover 2, a pressure plate 3, and a diaphragm spring 4.
- the clutch cover 2 is a substantially dish-shaped plate member having a circular opening 2a at the center, and the outer peripheral portion is fixed to the flywheel 51 by bolts, for example.
- the clutch cover 2 has a disk-shaped portion that is opposed to the outer peripheral portion of the flywheel 51 with a gap in the axial direction.
- the clutch cover 2 includes a clutch cover main body 11 constituting a main portion, a mounting flange portion 12 formed on the outer peripheral portion of the clutch cover main body 11, a plurality of tabs 13 for supporting the diaphragm spring 4, and And three accommodating portions 14 provided in the clutch cover main body 11.
- the inner peripheral part of the clutch cover main body 11 is continuous in an annular shape, and the inner peripheral edge is raised so as to protrude toward the axial transmission side by burring, thereby forming an annularly continuous collar part 11a.
- Each of the plurality of tabs 13 is formed by cutting out a part between the inner peripheral portion and the outer peripheral portion of the clutch cover main body 11 to form a punch hole 11b and bending it.
- the tab 13 includes a first support portion 13a extending from the clutch cover body 11 toward the axial direction engine side, and a second support portion 13b extending radially outward from the first support portion 13a.
- the plurality of punch holes 11b are formed independently. Therefore, a bridge portion 11c that connects the outer peripheral portion and the inner peripheral portion of the clutch cover main body 11 is formed between the adjacent punch holes 11b and 11b. Has been.
- the accommodating portion 14 is formed by embossing a part of the clutch cover main body 11 in a circular shape, and constitutes a part of a limiting mechanism described later.
- the pressure plate 3 is an annular member having a pressing surface 3 a formed on the side facing the flywheel 51. Between the pressing surface 3a and the flywheel 51, the friction member 53 of the clutch disk assembly 52 is disposed.
- the pressure plate 3 is formed with an annular protrusion 3b that protrudes in the axial direction on the side opposite to the pressing surface 3a.
- the pressure plate 3 is connected to the clutch cover 2 by a plurality of strap plates 7 so as to be movable in the axial direction but not relatively rotatable.
- the diaphragm spring 4 is a disk-shaped member disposed between the pressure plate 3 and the clutch cover 2, and includes an annular elastic portion 4a and a plurality of lever portions extending radially inward from the inner peripheral portion of the annular elastic portion 4a. 4b.
- the annular elastic portion 4 a is in contact with the protruding portion 3 b of the pressure plate 3.
- the inner peripheral portion of the annular elastic portion 4 a is supported on the tab 13 of the clutch cover 2 via a pair of wire rings 5. More specifically, a slit is formed between the plurality of lever portions 4b.
- the outer peripheral portion of the slit that is, the inner peripheral end portion of the annular elastic portion 4a and the base end portion (outer peripheral end portion) of the lever portion 4b. Is formed with a roughly oval hole 4c. And the 1st and 2nd support parts 13a and 13b of the tab 13 penetrate the hole 4c, respectively between the clutch cover main body 11 and the diaphragm spring 4, and between the diaphragm spring 4 and the 2nd support part 13b.
- the wiring 5 is arranged. Thereby, the annular elastic portion 4a of the diaphragm spring 4 can freely approach and leave the protruding portion 3b of the pressure plate 3 with the tab 13 and the wire ring 5 as fulcrums.
- a push-type release device (not shown) is engaged with the tip of the lever portion 4b of the diaphragm spring 4.
- This release device is composed of a release bearing or the like.
- the clutch cover assembly 1 of the present embodiment has a low release load characteristic realizing mechanism 8.
- the low release load characteristic realizing mechanism 8 is a mechanism for realizing a low release load characteristic even when wear of the friction member 53 progresses by flattening the pressing load characteristic.
- three low release load characteristic realizing mechanisms 8 are arranged side by side in the circumferential direction. For this reason, the mechanism 8 generates a load in a balanced manner in the circumferential direction.
- the low release load characteristic realization mechanism 8 is disposed at a position corresponding to the accommodating portion 14 of the clutch cover 2, and as shown in FIG. 3, a support bolt 22 as a support member, a cone spring 24 as an elastic member, It is composed of
- the support bolt 22 extends from the inner peripheral portion of the pressure plate 3 on the protruding portion 3b side to the axial transmission side.
- the support bolt 22 includes a body portion 22a, a head portion 22b having a larger outer diameter than the body portion 22a, and a flange portion 22c having a larger outer diameter than the head portion 22b.
- the trunk portion 22 a of the support bolt 22 extends further in the axial direction through the oblong hole 4 c of the diaphragm spring 4.
- the accommodating portion 14 of the clutch cover 2 has a shape that is recessed in a mortar shape on the axial engine side, and a hole 14 a is formed at a position corresponding to the support bolt 22 of the accommodating portion 14.
- the trunk portion 22 a of the support bolt 22 extends further in the axial direction through the hole 14 a, and as a result, the head portion 22 b of the support bolt 22 is located on the axial transmission side with respect to the housing portion 14.
- the cone spring 24 is accommodated on the axial transmission side of the accommodating portion 14 that is recessed in the axial direction.
- the outer peripheral edge of the cone spring 24 is supported by the outer peripheral edge of the accommodating portion 14.
- the inner peripheral edge of the cone spring 24 is supported by the flange portion 22 c of the support bolt 22.
- the cone spring 24 When the clutch is not worn, the cone spring 24 does not generate a load when the clutch is engaged. On the other hand, when the friction member 53 of the clutch disk assembly 52 is worn, the pressure plate 3 and the support bolt 22 are moved to the axial engine side, so that the cone spring 24 is located between the clutch cover 2 and the flange portion 22c of the support bolt 22. To apply a load in the axial direction to both members. The load applied by the cone spring 24 to the support bolt 22 or the like acts on the side opposite to the pressing load applied to the pressure plate 3 by the diaphragm spring 4, and the pressing load is reduced, and as a result, the release load is also kept low.
- FIG. 4 shows the load characteristic D of the diaphragm spring 4 and the wear margin of the friction member 53 of the present embodiment.
- the characteristic D of the diaphragm spring 4 has a peak portion d.
- the characteristic C of the cone spring 24 of the low release load characteristic realization mechanism 8 has an opposite peak part (a part projecting downward) that cancels the peak part d of the diaphragm spring 4, and the composite load is flat. Part H is formed.
- the cone spring 24 realizes the combined load flat portion H that secures a sufficiently large wear allowance.
- the clutch cover assembly 1 includes a restriction mechanism 30 that restricts the movement of the pressure plate 3 toward the flywheel 51 via the diaphragm spring 4.
- the limiting mechanism 30 includes a housing portion 14 of the clutch cover 2 and a lever portion 4 b of the diaphragm spring 4. That is, as described above, the accommodating portion 14 has a shape that is recessed in the shape of a mortar on the axial direction engine side. Therefore, when the diaphragm spring 4 moves to the axial direction transmission side, the diaphragm spring 4 The lever portion 4b can contact the side surface of the housing portion 14 on the axial direction engine side.
- the maximum allowable wear amount of the friction member 53 means the maximum wear amount within a range in which the friction member 53 can exhibit a desired torque transmission characteristic, and from the set line S to the wear line W shown in FIG. This is equivalent to the wear allowance.
- the lever portion 4b of the diaphragm spring 4 is brought into contact with the engine side surface of the housing portion 14 to restrict the movement of the pressure plate 3 to the flywheel side. It is not limited.
- the lever portion 4 b may be brought into contact with the inner peripheral end portion of the clutch cover 2.
- the deformation of the clutch cover is suppressed, and the amount of deflection of the clutch cover is reduced. Therefore, a clutch cover assembly with improved clutch disengagement performance can be obtained.
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- General Engineering & Computer Science (AREA)
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Abstract
Description
図1にクラッチカバー組立体1の縦断面概略図、図2にクラッチカバー組立体1の平面概略図を示す。図中に示すO-O線が、フライホイール51及びクラッチカバー組立体1の回転軸線である。以下、図の左側を軸方向エンジン側といい、図の右側を軸方向トランスミッション側という。
クラッチカバー2は、中心部に円形の開口2aを有する概ね皿形状のプレート部材であり、外周部が例えばボルトによりフライホイール51に固定されるようになっている。このクラッチカバー2は、フライホイール51の外周部に対して軸方向に隙間をあけて対向する円板状部分を有している。より詳細には、クラッチカバー2は、主要部を構成するクラッチカバー本体11と、クラッチカバー本体11の外周部に形成された取付フランジ部12と、ダイヤフラムスプリング4を支持する複数のタブ13と、クラッチカバー本体11に設けられた3つの収容部14と、を有している。
プレッシャープレート3は、フライホイール51に対向する側に押圧面3aが形成された環状の部材である。押圧面3aとフライホイール51との間には、クラッチディスク組立体52の摩擦部材53が配置される。プレッシャープレート3には、押圧面3aと反対側に軸方向に突出する環状の突出部3bが形成されている。プレッシャープレート3は、複数のストラッププレート7によって、クラッチカバー2に対して、軸方向には移動可能であるが相対回転不能に連結されている。
ダイヤフラムスプリング4は、プレッシャープレート3とクラッチカバー2との間に配置された円板状部材であり、環状弾性部4aと、環状弾性部4aの内周部から径方向内側に延びる複数のレバー部4bとから構成されている。環状弾性部4aはプレッシャープレート3の突出部3bに当接している。環状弾性部4aの内周部は1対のワイヤリング5を介してクラッチカバー2のタブ13に支持されている。より詳細には、複数のレバー部4bの間にはスリットが形成され、このスリットの外周部、すなわち環状弾性部4aの内周端部であってレバー部4bの基端部(外周端部)には、概略小判状の孔4cが形成されている。そして、タブ13の第1及び第2支持部13a,13bは孔4cを貫通し、クラッチカバー本体11とダイヤフラムスプリング4との間、及びダイヤフラムスプリング4と第2支持部13bとの間のそれぞれに、ワイヤリング5が配置されている。これにより、ダイヤフラムスプリング4の環状弾性部4aは、タブ13及びワイヤリング5を支点として、プレッシャープレート3の突出部3bに対して接近、離反自在となっている。
本実施形態のクラッチカバー組立体1は、低レリーズ荷重特性実現機構8を有している。この低レリーズ荷重特性実現機構8は、押付荷重特性を平坦化することで、摩擦部材53の摩耗が進んだ場合でも低レリーズ荷重特性を実現するための機構である。本実施形態においては、3つの低レリーズ荷重特性実現機構8が円周方向に並んで配置されている。このため、機構8は円周方向においてバランスよく荷重を発生する。
このクラッチカバー組立体1は、ダイヤフラムスプリング4を介してプレッシャープレート3のフライホイール51側への移動を制限する制限機構30を備えている。具体的には図3に示すように、制限機構30は、クラッチカバー2の収容部14と、ダイヤフラムスプリング4のレバー部4bとから構成されている。すなわち、収容部14は、前述のように、軸方向エンジン側にすり鉢状にくぼんだ形状を有しており、このため、ダイヤフラムスプリング4が軸方向トランスミッション側に移動した場合に、ダイヤフラムスプリング4のレバー部4bが収容部14の軸方向エンジン側の側面に当接可能となっている。
このクラッチカバー組立体1では、図示しないレリーズ装置がダイヤフラムスプリング4のレバー部4bの先端に荷重を与えていない状態で、環状弾性部4aはプレッシャープレート3に押圧荷重を与えている。その結果、クラッチディスク組立体52の摩擦部材53がフライホイール51に押し付けられ、クラッチディスク組立体52にトルクが伝達される(クラッチオン状態)。
(a) 前記実施形態では、ダイヤフラムスプリング4のレバー部4bを収容部14のエンジン側側面に当接させてプレッシャープレート3のフライホイール側への移動を制限したが、制限機構の構成はこれに限定されない。例えば、レバー部4bをクラッチカバー2の内周端部に当接させるようにしてもよい。
2 クラッチカバー
2a 開口
3 プレッシャープレート
4 ダイヤフラムスプリング
11 クラッチカバー本体
11a つば部
11b 抜き孔
11c ブリッジ部
13 タブ
14 収容部
24 コーンスプリング
30 制限機構
12 支持ボルト(支持部材)
51 フライホイール
52 クラッチディスク組立体
53 摩擦部材
Claims (8)
- エンジンのフライホイールにクラッチディスク組立体の摩擦部材を押し付け及び押し付け解除するためのクラッチカバー組立体であって、
前記フライホイールに固定可能であり、中心部に円形の開口を有するとともに、内周部と外周部との間に前記フライホイール側に折り曲げられかつ外周側に折り曲げられて形成された複数のタブを有し、内周縁部が環状に連続しているクラッチカバーと、
前記クラッチカバーに対して相対回転不能に連結され、前記フライホイールとの間で前記摩擦部材を挟むためのプレッシャープレートと、
前記クラッチカバーの複数のタブに支持され、前記プレッシャープレートを前記フライホイール側に付勢するダイヤフラムスプリングと、
を備えたクラッチカバー組立体。 - 前記クラッチカバーの内周縁部には、軸方向において前記フライホイールから離れる側に突出し環状に連続するつば部が形成されている、請求項1に記載のクラッチカバー組立体。
- 前記複数のタブとともに前記ダイヤフラムスプリングを支持する1対のワイヤリングをさらに備えた、請求項1に記載のクラッチカバー組立体。
- 前記クラッチカバーには、複数の前記タブを形成するための複数の抜き孔が形成されるとともに、複数の前記抜き孔はそれぞれ隣接する抜き孔と独立して形成されており、隣接する前記抜き孔の間には、外周部と内周部とを連結するブリッジ部が形成されている、
請求項1に記載のクラッチカバー組立体。 - 前記クラッチカバーに支持され、前記ダイヤフラムスプリングの付勢力に対抗する荷重を発生する少なくとも1つの弾性部材と、
前記プレッシャープレートの前記フライホイール側への移動を一定の範囲内に制限する制限機構と、をさらに備え、
前記クラッチカバーは、前記フライホイールに固定される固定部と、前記固定部の半径方向内側に配置される部分であって、前記プレッシャープレート側にくぼみ、前記弾性部材を収容する少なくとも1つの収容部を有しており、
前記制限機構は、前記ダイヤフラムスプリングが前記クラッチカバーに当接することにより実現されており、
前記弾性部材は、前記ダイヤフラムスプリングの前記プレッシャープレートと軸方向反対側に配置されている、
請求項1に記載のクラッチカバー組立体。 - 前記制限機構は、前記ダイヤフラムスプリングが前記収容部に当接することにより実現されている、
請求項5に記載のクラッチカバー組立体。 - 前記制限機構は、前記ダイヤフラムスプリングが前記クラッチカバーの内周端部に当接することにより実現されている、
請求項5に記載のクラッチカバー組立体。 - 前記制限機構により制限された前記プレッシャープレートの軸方向位置は、前記摩擦部材の摩耗量が最大許容摩耗量に達した状態における前記プレッシャープレートの押圧位置に対応している、
請求項5に記載のクラッチカバー組立体。
Priority Applications (3)
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CN2010800450018A CN102575721A (zh) | 2009-10-15 | 2010-09-03 | 离合器盖组件 |
US13/501,928 US20120199435A1 (en) | 2009-10-15 | 2010-09-03 | Clutch cover assembly |
DE112010004054.0T DE112010004054B4 (de) | 2009-10-15 | 2010-09-03 | Kupplungsabdeckungsanordnung |
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JP2009-237878 | 2009-10-15 | ||
JP2009237878A JP2011085181A (ja) | 2009-10-15 | 2009-10-15 | クラッチカバー組立体 |
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JP (1) | JP2011085181A (ja) |
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DE112013004697A5 (de) * | 2012-09-25 | 2015-07-02 | Schaeffler Technologies AG & Co. KG | Reibungskupplung |
DE102014211023A1 (de) * | 2014-06-10 | 2015-12-17 | Schaeffler Technologies AG & Co. KG | Kupplungsvorrichtung |
DE102015219734B3 (de) * | 2015-10-12 | 2017-02-02 | Schaeffler Technologies AG & Co. KG | Deckelanordnung für eine Reibungskupplung und Kraftfahrzeug |
JP2018053914A (ja) * | 2016-09-26 | 2018-04-05 | 株式会社エクセディ | クラッチカバー |
DE102016223507A1 (de) | 2016-11-28 | 2018-05-30 | Schaeffler Technologies AG & Co. KG | Deckelanordnung für eine Reibungskupplung |
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JPS62209226A (ja) * | 1986-03-10 | 1987-09-14 | Daikin Mfg Co Ltd | クラツチカバ−組立体 |
JPH1182536A (ja) * | 1997-09-05 | 1999-03-26 | Unisia Jecs Corp | クラッチ装置ユニット |
JP2002523275A (ja) * | 1998-08-21 | 2002-07-30 | ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト | 駆動系統 |
JP2004278743A (ja) * | 2003-03-18 | 2004-10-07 | Exedy Corp | クラッチカバー組立体 |
JP2005195077A (ja) * | 2004-01-06 | 2005-07-21 | Exedy Corp | クラッチカバー組立体 |
JP2006029415A (ja) * | 2004-07-14 | 2006-02-02 | Exedy Corp | クラッチカバー組立体及びその製造方法 |
JP2007162756A (ja) * | 2005-12-09 | 2007-06-28 | Exedy Corp | クラッチカバー組立体 |
JP2007198462A (ja) * | 2006-01-25 | 2007-08-09 | Exedy Corp | クラッチカバー組立体 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3939951A (en) * | 1974-12-23 | 1976-02-24 | Dana Corporation | Diaphragm clutch spring having radial and rotational restraints |
DE2843289A1 (de) * | 1978-10-04 | 1980-04-17 | Luk Lamellen & Kupplungsbau | Reibungskupplung |
DE4420251B4 (de) * | 1993-06-23 | 2006-03-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Reibungskupplung |
JP2007198507A (ja) | 2006-01-26 | 2007-08-09 | Exedy Corp | クラッチカバー組立体 |
JP2008128260A (ja) * | 2006-11-16 | 2008-06-05 | Exedy Corp | クラッチカバー組立体 |
-
2009
- 2009-10-15 JP JP2009237878A patent/JP2011085181A/ja active Pending
-
2010
- 2010-09-03 US US13/501,928 patent/US20120199435A1/en not_active Abandoned
- 2010-09-03 CN CN2010800450018A patent/CN102575721A/zh active Pending
- 2010-09-03 WO PCT/JP2010/065109 patent/WO2011045987A1/ja active Application Filing
- 2010-09-03 DE DE112010004054.0T patent/DE112010004054B4/de active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62209226A (ja) * | 1986-03-10 | 1987-09-14 | Daikin Mfg Co Ltd | クラツチカバ−組立体 |
JPH1182536A (ja) * | 1997-09-05 | 1999-03-26 | Unisia Jecs Corp | クラッチ装置ユニット |
JP2002523275A (ja) * | 1998-08-21 | 2002-07-30 | ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト | 駆動系統 |
JP2004278743A (ja) * | 2003-03-18 | 2004-10-07 | Exedy Corp | クラッチカバー組立体 |
JP2005195077A (ja) * | 2004-01-06 | 2005-07-21 | Exedy Corp | クラッチカバー組立体 |
JP2006029415A (ja) * | 2004-07-14 | 2006-02-02 | Exedy Corp | クラッチカバー組立体及びその製造方法 |
JP2007162756A (ja) * | 2005-12-09 | 2007-06-28 | Exedy Corp | クラッチカバー組立体 |
JP2007198462A (ja) * | 2006-01-25 | 2007-08-09 | Exedy Corp | クラッチカバー組立体 |
Also Published As
Publication number | Publication date |
---|---|
JP2011085181A (ja) | 2011-04-28 |
DE112010004054B4 (de) | 2018-03-22 |
US20120199435A1 (en) | 2012-08-09 |
CN102575721A (zh) | 2012-07-11 |
DE112010004054T5 (de) | 2012-11-29 |
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