JP2703977B2 - 2 mass flywheel for clutch device - Google Patents
2 mass flywheel for clutch deviceInfo
- Publication number
- JP2703977B2 JP2703977B2 JP1043349A JP4334989A JP2703977B2 JP 2703977 B2 JP2703977 B2 JP 2703977B2 JP 1043349 A JP1043349 A JP 1043349A JP 4334989 A JP4334989 A JP 4334989A JP 2703977 B2 JP2703977 B2 JP 2703977B2
- Authority
- JP
- Japan
- Prior art keywords
- inertial
- friction
- disks
- disk
- friction element
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000013016 damping Methods 0.000 claims description 42
- 239000012530 fluid Substances 0.000 claims description 17
- 230000007717 exclusion Effects 0.000 claims description 15
- 238000003466 welding Methods 0.000 claims description 2
- 230000002093 peripheral effect Effects 0.000 description 9
- 230000005540 biological transmission Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
Classifications
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/139—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by friction-damping means
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/0052—Physically guiding or influencing
- F16F2230/0064—Physically guiding or influencing using a cam
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、クラッチ装置用２質量フライホイールに関
するものである。Description: TECHNICAL FIELD The present invention relates to a two-mass flywheel for a clutch device.
自動車駆動装置の一部をなす２質量フライホイールと
して構成されたクラッチ装置が、西ドイツ国特許公開公
報第3418671号に開示されている。この公知のクラッチ
装置は、２つの慣性円板間の摩擦によって生じる減衰力
を変化させることができるようになっている。この減衰
力の変化は、フライホイールの回転速度変化に応じて引
き起こされ、これによって望ましくない共振の発生が防
止される。A clutch device configured as a two-mass flywheel that forms part of a motor vehicle drive is disclosed in DE-A-3418671. This known clutch device is capable of changing the damping force generated by friction between two inertial disks. This change in damping force is caused in response to a change in the rotational speed of the flywheel, thereby preventing the occurrence of undesirable resonance.
この公知のクラッチ装置の欠点は、回転速度は別とし
て、原動機の運転状態の違いが考慮されていないことに
ある。特に、このクラッチ装置は、原動機の運転負荷の
大小を判別することができない。A disadvantage of this known clutch device is that, apart from the rotational speed, differences in the operating state of the prime mover are not taken into account. In particular, this clutch device cannot determine the magnitude of the operation load of the prime mover.
西ドイツ国特許公開公報第3447926号に開示されたク
ラッチ装置では、２つの慣性円板間の相対回転角度が特
定の角度を経た後に、その摩擦減衰装置が有効に作用す
るようになっている。これによると、原動機の各種運転
条件に減衰効果を適合させることができる。しかしなが
ら、これの場合は、相対回転角度が小さい領域、例えば
原動機の無負荷運転中には減衰力が有効に作用せず、相
対回転角度が特定角度を超えた時点で減衰力が急激に作
用するという欠点がある。In the clutch device disclosed in German Offenlegungsschrift 3447926, the friction damping device works effectively after the relative rotation angle between the two inertial disks has passed a certain angle. According to this, the damping effect can be adapted to various operating conditions of the prime mover. However, in this case, the damping force does not effectively act in a region where the relative rotation angle is small, for example, during the no-load operation of the prime mover, and the damping force suddenly acts when the relative rotation angle exceeds a specific angle. There is a disadvantage that.
西ドイツ国特許公開公報第2848748号には、減衰媒体
を充填した排除室内にピストン体を配置することによ
り、流体減衰を行うようにしたクラッチ装置が開示され
ている。このものは、流体通路の絞り間隙が、連続的又
は段階的に変化し得るようになっているが、これは相対
回転角度が極めて大きい範囲でのみ有効である。West German Patent Publication No. 2848748 discloses a clutch device in which a piston body is arranged in an exclusion chamber filled with a damping medium to perform fluid damping. In this case, the throttle gap of the fluid passage can be changed continuously or stepwise, but this is effective only in a range where the relative rotation angle is extremely large.
このような従来技術の問題点に鑑み、本発明の目的
は、２つの慣性円板間に作用する減衰力を、回転速度に
関わりなく、原動機の負荷条件に適合させることができ
るように改良されたクラッチ装置用２質量フライホイー
ルを提供することにある。In view of such problems of the prior art, it is an object of the present invention to improve a damping force acting between two inertial disks so that the damping force can be adapted to a load condition of a prime mover regardless of a rotation speed. To provide a two-mass flywheel for a clutch device.
このような目的を達成するために、本発明において
は、相対回転角度が変化し得るように弾性的に相互連結
された２つの慣性円板と、これら２つの慣性円板間に設
けられて両慣性円板間に摩擦圧接力を作用させるための
摩擦要素と、一方の慣性円板を受容しかつ減衰媒体を充
填するべく他方の慣性円板に画成された液密空間と、該
液密空間内に画定された排除室内を前記２つの慣性円板
間の相対回転に応じて周方向に移動して流体減衰力を発
生させるためのピストン要素とを備えたクラッチ装置用
２質量フライホイールを、前記摩擦要素は、回転中心か
らの半径方向距離が周方向について変化するように前記
２つの慣性円板のうちの少なくともいずれか一方に形成
された摩擦面と、その他方の慣性円板に径方向に移動可
能に設けられ、かつ前記摩擦面に常時摺接するようにば
ね手段で弾発付勢された可動部材とからなるものとする
と共に、前記２つの慣性円板間の相対回転角度の変化に
応じた前記可動部材の半径方向移動に応じて前記排除室
と前記可動部材との対向面間の間隙寸法が変化するよう
に構成することにより、前記ピストン要素の機能を前記
可動部材に担わせるものとした。In order to achieve such an object, in the present invention, two inertial disks elastically interconnected so that the relative rotation angle can be changed, and both inertial disks provided between these two inertial disks are provided. A friction element for applying a friction welding force between the inertial disks; a liquid-tight space defined in the other inertial disk for receiving one inertial disk and filling the damping medium; A two-mass flywheel for a clutch device having a piston element for generating a fluid damping force by moving circumferentially in an exclusion chamber defined in a space in accordance with relative rotation between the two inertial disks. A friction surface formed on at least one of the two inertial disks so that a radial distance from a rotation center changes in a circumferential direction; and a friction surface formed on the other inertial disk. To be movable in the direction A movable member which is resiliently urged by a spring means so as to always slide on the friction surface, and wherein the movable member is moved radially in accordance with a change in a relative rotation angle between the two inertial disks. The function of the piston element is assigned to the movable member by changing the gap dimension between the opposing surfaces of the exclusion chamber and the movable member in accordance with the above.
これによれば、原動機の負荷トルク変化の影響を考慮
することが可能となる。つまり、減衰力は、回転速度に
関わりなく、２つの慣性円板間の相対回転角度変化の影
響、すなわち負荷トルク変化の影響を受けることとな
る。特に摩擦面の輪郭を適宜な形状とすることにより、
負荷トルク変化に応じた減衰力特性を、任意の設定とす
ることができる。また、このフライホイールは、機械的
な摩擦減衰力と、流体力学的な流体減衰力とを、１つの
可動部材にて制御し得る点が最も重要な特徴である。つ
まり、本発明装置においては、２つの慣性円板間の相対
回転角度変化に伴って半径方向に移動する可動部材が、
摩擦要素としてだけでなく、流体中を移動して抵抗力を
受けるピストン要素としても働き、しかも流体減衰力の
元になる絞り間隙の寸法も変化させる。これらのことか
ら、このフライホイールによれば、原動機の運転状態の
変化に対して減衰力を十分に適合させることができる。According to this, it is possible to consider the influence of the change in the load torque of the prime mover. That is, the damping force is affected by the change in the relative rotation angle between the two inertial disks, that is, the change in the load torque, regardless of the rotation speed. In particular, by making the contour of the friction surface an appropriate shape,
The damping force characteristic according to the load torque change can be set arbitrarily. The most important feature of the flywheel is that the mechanical friction damping force and the hydrodynamic fluid damping force can be controlled by one movable member. That is, in the device of the present invention, the movable member that moves in the radial direction with a change in the relative rotation angle between the two inertial disks is
It acts not only as a friction element, but also as a piston element that moves in the fluid and receives a resistance force, and also changes the size of the throttle gap, which is the source of the fluid damping force. From these facts, according to this flywheel, the damping force can be sufficiently adapted to changes in the operating state of the prime mover.
以下、添付図面に示した実施例に基づいて本発明につ
いて詳細に説明する。Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
第１図に示すクラッチ装置１は、西ドイツ国特許公開
公報第2848748号に開示されたものと基本構成は実質的
に同じであり、トルク伝達のために、図示省略した弾性
要素を介して相互結合された第１慣性円板２と第２慣性
円板３とを備えている。The clutch device 1 shown in FIG. 1 has substantially the same basic configuration as that disclosed in the German Offenlegungsschrift No. 2848748, and is interconnected via a resilient element (not shown) for torque transmission. The first inertial disk 2 and the second inertial disk 3 are provided.
第１慣性円板２には、クラッチ装置の基本構造に合わ
せて円板状に構成した第１摩擦要素４が設けられてい
る。この第１摩擦要素４の半径方向外側の表面に、円周
方向に沿う摩擦面６が設けられている。この摩擦面６の
回転中心からの距離ｒは、円周方向について一定ではな
く、両慣性円板２・３間の相対回転角度ａに応じて変化
するように定められている。The first inertial disk 2 is provided with a first friction element 4 configured in a disk shape in accordance with the basic structure of the clutch device. A radially outer surface of the first friction element 4 is provided with a friction surface 6 along the circumferential direction. The distance r of the friction surface 6 from the center of rotation is not constant in the circumferential direction, but is determined so as to change according to the relative rotation angle a between the inertial disks 2 and 3.
２つの側板を備えた第２慣性円板３は、第１慣性円板
２を受容する液密な空間14を画成すると共に、摩擦面７
を備えた第２摩擦要素５（請求の範囲に記載の可動部材
に対応）と結合されている。この第２摩擦要素５の摩擦
面７は、第１摩擦要素４の摩擦面６に接触している。The second inertial disc 3 with two side plates defines a liquid-tight space 14 for receiving the first inertial disc 2 and a friction surface 7.
And the second friction element 5 (corresponding to the movable member described in the claims). The friction surface 7 of the second friction element 5 is in contact with the friction surface 6 of the first friction element 4.
第２摩擦要素５は、第２図に詳細に示すように、断面
形状がＵ字形をなしており、その脚部18は、第２慣性円
板３の２つの側板間を連結するように、２つの側板の互
いに対向する内面に結合した角形ブロック10の周方向両
側の案内面19にて規制され、半径方向に移動可能になっ
ている。As shown in detail in FIG. 2, the second friction element 5 has a U-shaped cross section, and its legs 18 are connected so as to connect between two side plates of the second inertial disk 3. The two side plates are restricted by guide surfaces 19 on both sides in the circumferential direction of the rectangular block 10 connected to the inner surfaces of the two side plates facing each other, and are movable in the radial direction.
角形ブロック10の内周側と、Ｕ字形をなす第２摩擦要
素５の底部との間には、波板ばね12が設けられている。
これにより、第２摩擦要素５は、回転中に作用する遠心
力に抗して半径方向内方に弾発付勢され、その摩擦面７
を、第１摩擦要素４の摩擦面６に常時押し当てている。A corrugated spring 12 is provided between the inner peripheral side of the rectangular block 10 and the bottom of the U-shaped second friction element 5.
As a result, the second friction element 5 is elastically urged inward in the radial direction against the centrifugal force acting during rotation, and its friction surface 7
Is constantly pressed against the friction surface 6 of the first friction element 4.
第２慣性円板３の２つの側板間の内部空間14内には、
液密の排除室13が画成されている。そして、角形ブロッ
ク10によって案内された第２摩擦要素５は、減衰媒体中
で抵抗を受けるピストン要素の機能を担っている。In the internal space 14 between the two side plates of the second inertial disk 3,
A liquid-tight exclusion chamber 13 is defined. The second friction element 5 guided by the square block 10 then fulfills the function of a piston element which resists in the damping medium.
第２摩擦要素５の脚部18の半径方向外端と、第２慣性
円板３の外周壁で画定された排除室13の内周面との間に
は、流体減衰度を決定する絞り間隙17が形成されてい
る。A throttle gap for determining the degree of fluid damping is provided between the radially outer end of the leg 18 of the second friction element 5 and the inner peripheral surface of the exclusion chamber 13 defined by the outer peripheral wall of the second inertial disk 3. 17 are formed.
以上のようにして、第２摩擦要素５は、２つの機能、
つまり、第１摩擦要素４の摩擦面６に自身の摩擦面７を
摺接させることで第１・第２両慣性円板２・３間に摩擦
減衰力を発生させる機能と、流体が移動する絞り間隙17
を排除室13内に形成すると共に、自身が円周方向に移動
する際に流体減衰力を発生させるピストン要素としての
機能とを果たす。As described above, the second friction element 5 has two functions,
That is, a function of generating a friction damping force between the first and second inertial disks 2 and 3 by sliding the friction surface 7 of the first friction element 4 against the friction surface 6 of the first friction element 4, and the fluid moves. Aperture gap 17
Is formed in the exclusion chamber 13 and also functions as a piston element that generates a fluid damping force when it moves in the circumferential direction.
既に述べたように、第１摩擦要素４の摩擦面６の回転
中心からの距離ｒは、周方向について均一ではないの
で、第１・第２両慣性円板２・３間の相対回転角度の変
化に応じ、第２摩擦要素５は案内面19に沿って半径方向
に移動する。その際、波板ばね12の働きで、第２摩擦要
素５は、第１摩擦要素４の摩擦面６に持続的に当接する
が、波板ばね12の撓み量の変化に連れて、第２摩擦要素
５の摩擦面６に対する押圧力、すなわち摩擦減衰力が変
化する。また、第２摩擦要素５の半径方向移動に伴って
絞り間隙17の寸法も変化する。従って、摩擦減衰力と共
に流体減衰力も変化する。As described above, since the distance r of the friction surface 6 of the first friction element 4 from the center of rotation is not uniform in the circumferential direction, the relative rotation angle between the first and second inertial disks 2 and 3 is determined. In response to the change, the second friction element 5 moves radially along the guide surface 19. At that time, the second friction element 5 is continuously in contact with the friction surface 6 of the first friction element 4 by the action of the corrugated spring 12, but the second friction element 5 The pressing force of the friction element 5 against the friction surface 6, that is, the friction damping force changes. In addition, the size of the throttle gap 17 changes with the radial movement of the second friction element 5. Therefore, the fluid damping force changes together with the friction damping force.
第３図は、排除室13内における第２摩擦要素５付近の
縦断面である。この図には、中央円板2aと両側円板2bと
で構成された第１慣性円板２が示されている。中央円板
2aと両側円板2bとは、第１・第２両慣性円板２・３と同
様に、図示省略した例えばばねなどの弾性要素を介して
互いに結合されている。本実施例においては、実質的に
中央円板2aの外周面に第１摩擦要素４が設けられてい
る。FIG. 3 is a vertical cross section of the vicinity of the second friction element 5 in the exclusion chamber 13. FIG. 1 shows a first inertial disk 2 composed of a center disk 2a and both-side disks 2b. Central disk
Like the first and second inertial disks 2 and 3, the two disks 2a and the both-side disks 2b are connected to each other via an elastic element such as a spring (not shown). In this embodiment, the first friction element 4 is provided substantially on the outer peripheral surface of the central disk 2a.
両側円板2bの外周面は、排除室13の内周側境界壁を形
成しており、両側円板2bと第２摩擦要素５との相互対向
面間の間隙17aの寸法は比較的大きくなっている。The outer peripheral surface of both side disks 2b forms an inner peripheral side boundary wall of the exclusion chamber 13, and the size of the gap 17a between the mutually opposing surfaces of the both side disks 2b and the second friction element 5 becomes relatively large. ing.
第４図は、第１慣性円板２に設けられた第１摩擦要素
４の外周輪郭８の概略展開図である。同図において、第
１・第２両慣性円板２・３間の相対回転角度が零のと
き、すなわち、原動機が無負荷運転時には、第２摩擦要
素５は、第１摩擦要素４の摩擦面６に距離ｒをおいて接
している。この場合、第２摩擦要素５は、排除室13の比
較的内周側にあり、流体減衰用の絞り間隙17は大きく開
いている。FIG. 4 is a schematic development view of the outer peripheral contour 8 of the first friction element 4 provided on the first inertial disk 2. In the figure, when the relative rotation angle between the first and second inertial disks 2 and 3 is zero, that is, when the prime mover is in a no-load operation, the second friction element 5 becomes the friction surface of the first friction element 4. 6 at a distance r. In this case, the second friction element 5 is relatively on the inner peripheral side of the exclusion chamber 13, and the throttle gap 17 for fluid attenuation is largely open.
第１・第２両慣性円板２・３間で角度ａだけ相対回転
すると、第２摩擦要素５の回転中心からの距離はｒ′で
示された寸法となる。つまり、この時の第２摩擦要素５
の半径方向変位量はｒ′−ｒとなり、その際、波板ばね
12は、角形ブロック10と第２摩擦要素５との間で一層圧
縮されるので、両摩擦面６・７には、減衰力の高まりに
相当する一層高い圧力が加わる。これと同時に、第２摩
擦要素５と排除室13との対向面間の絞り間隙17も、同一
量だけ狭くなり、流体減衰力が強まる。When the first and second inertial disks 2 and 3 rotate relative to each other by the angle a, the distance from the rotation center of the second friction element 5 becomes a dimension indicated by r '. That is, the second friction element 5 at this time
Is r'-r, and the corrugated spring
12 is further compressed between the rectangular block 10 and the second friction element 5, so that a higher pressure is applied to both friction surfaces 6, 7 corresponding to the increased damping force. At the same time, the throttle gap 17 between the opposing surfaces of the second friction element 5 and the exclusion chamber 13 also becomes smaller by the same amount, and the fluid damping force increases.
さらに高い負荷トルクの作用を受けて、第１・第２両
慣性円板２・３間が角度ｂだけ相対回転すると、第２摩
擦要素５は、さらに半径方向外向きに移動し、両摩擦面
６・７に作用する摩擦減衰力がより一層強まる。と同時
に、流体減衰力を支配する絞り間隙17もなお一層狭くな
る。When the first and second inertial disks 2 and 3 rotate relative to each other by an angle b under the action of a higher load torque, the second friction element 5 further moves outward in the radial direction, and The friction damping force acting on 6.7 is further enhanced. At the same time, the throttle gap 17 that governs the fluid damping force becomes even smaller.
このようにして、摩擦減衰力と流体減衰力との併合に
より、原動機の回転速度に関わりなく、負荷状態に適合
した減衰作用を得ることができる。その際、重要なこと
は、第１摩擦要素４上の摩擦面６の外周輪郭８である。
この輪郭８により、第２摩擦要素５の半径方向位置が第
１・第２両慣性円板２・３間の相対回転角度に応じて変
化するので、摩擦減衰力と流体減衰力とを共に制御する
ことが可能となる。In this way, by combining the friction damping force and the fluid damping force, it is possible to obtain a damping action suitable for the load state regardless of the rotation speed of the prime mover. What is important here is the outer contour 8 of the friction surface 6 on the first friction element 4.
The contour 8 changes the radial position of the second friction element 5 according to the relative rotation angle between the first and second inertial disks 2 and 3, so that both the friction damping force and the fluid damping force are controlled. It is possible to do.
また第３図は、第１摩擦要素４における両側円板2b用
の輪郭8aを示している。第２摩擦要素５が、第１摩擦要
素４、つまり第１慣性円板２の中央円板2aとだけ接触し
ているので、側円板2bの外周面の輪郭8aは、第２摩擦要
素５より半径方向内側にある間隙17aをやはり周方向に
変化させるのに利用することができる。この輪郭8aは、
相対回転角度が零の範囲のときに間隙17aを大とし、無
負荷運転範囲から定格負荷運転範囲に移行する部分は斜
面20の形で間隙17aを徐々に狭くし、高負荷運転範囲に
移行する部分は別の斜面21の形で再び間隙17aを徐々に
狭くするようになっている。従って、第１慣性円板２
が、中央円板2aと側円板2bからなるものであると、摩擦
減衰力と流体減衰力とを別々に調整することが可能とな
る。この場合、第１摩擦要素４として使用されるのは、
第１慣性円板２を形成する円板のうち、運転中の回転角
変化量が大きくなる方である。FIG. 3 shows a profile 8a for the two-sided disk 2b in the first friction element 4. Since the second friction element 5 is in contact only with the first friction element 4, that is, the center disk 2a of the first inertial disk 2, the contour 8a of the outer peripheral surface of the side disk 2b is The radially inner gap 17a can also be used to vary circumferentially. This contour 8a
When the relative rotation angle is in the range of zero, the gap 17a is made large, and in the portion where the operation shifts from the no-load operation range to the rated load operation range, the gap 17a is gradually narrowed in the form of the slope 20, and the operation shifts to the high load operation range. The portion is again in the form of another slope 21 to gradually narrow the gap 17a again. Therefore, the first inertial disk 2
However, if it is composed of the center disk 2a and the side disk 2b, the friction damping force and the fluid damping force can be adjusted separately. In this case, what is used as the first friction element 4 is
One of the disks forming the first inertial disk 2 has a larger rotation angle change amount during operation.
以上のようにして、第１・第２両慣性円板２・３間の
相対回転角度変位が零のときは減衰力も事実上零とし、
第１・第２両慣性円板２・３間の相対回転角度が増すの
に従って緩やかに、或いは累進的に減衰力を強め、最終
段階においては、減衰力を再度低下又はさらに上昇させ
ることができる。As described above, when the relative rotational angular displacement between the first and second inertial disks 2 and 3 is zero, the damping force is also substantially zero,
As the relative rotation angle between the first and second inertial disks 2 and 3 increases, the damping force is increased gradually or progressively, and in the final stage, the damping force can be reduced again or further increased. .
第１図は、排除室と摩擦減衰装置とを有する本発明によ
るクラッチの要部断面図である。 第２図は、排除室の拡大縦断面図である。 第３図は、２つの部分からなる第１慣性円板を有するフ
ライホイールの要部縦断面図である。 第４図は、摩擦面の輪郭の概要展開図である。 １…クラッチ、２・３…慣性円板、2a・2b…円板、４・
５…摩擦要素、６・７…摩擦面、８・8a…輪郭、10…角
形ブロック、12…ばね、13…排除室、14…空間、17・17
a…間隙、18…脚部、19…案内面、20・21…斜面FIG. 1 is a sectional view of a main part of a clutch according to the present invention having an exclusion chamber and a friction damping device. FIG. 2 is an enlarged vertical sectional view of the exclusion chamber. FIG. 3 is a longitudinal sectional view of a main part of a flywheel having a first inertial disk composed of two parts. FIG. 4 is a schematic development view of the outline of the friction surface. 1. Clutch, 2.3: Inertial disk, 2a, 2b: Disk, 4.
5 friction element, 6/7 friction surface, 8.8a contour, 10 square block, 12 spring, 13 exclusion chamber, 14 space, 17/17
a… Gap, 18… Leg, 19… Guideway, 20 ・ 21… Slope
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭61−282640（ＪＰ，Ａ) 特開 昭55−65728（ＪＰ，Ａ) 実開 昭61−161449（ＪＰ，Ｕ) ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-61-282640 (JP, A) JP-A-55-65728 (JP, A)
Claims (1)
相互連結された２つの慣性円板と、これら２つの慣性円
板間に設けられて両慣性円板間に摩擦圧接力を作用させ
るための摩擦要素と、一方の慣性円板を受容しかつ減衰
媒体を充填するべく他方の慣性円板に画成された液密空
間と、該液密空間内に画定された排除室内を前記２つの
慣性円板間の相対回転に応じて周方向に移動して流体減
衰力を発生させるためのピストン要素とを備えたクラッ
チ装置用２質量フライホイールであって、 前記摩擦要素は、回転中心からの半径方向距離が周方向
について変化するように前記２つの慣性円板のうちの少
なくともいずれか一方に形成された摩擦面と、その他方
の慣性円板に径方向に移動可能に設けられ、かつ前記摩
擦面に常時摺接するようにばね手段で弾発付勢された可
動部材とからなり、 前記２つの慣性円板間の相対回転角度の変化に応じた前
記可動部材の半径方向移動に応じて前記排除室と前記可
動部材との対向面間の間隙寸法が変化するようにするこ
とにより、前記ピストン要素の機能を前記可動部材に担
わせるものとしたことを特徴とするクラッチ装置用２質
量フライホイール。An inertial disk elastically interconnected so that a relative rotation angle can be changed, and a friction welding force is provided between the two inertial disks provided between the two inertial disks. A friction element for receiving the inertial disk, a liquid-tight space defined in the other inertial disk for filling the damping medium, and an exclusion chamber defined in the liquid-tight space. A piston element for generating a fluid damping force by moving in a circumferential direction according to a relative rotation between two inertial disks, wherein the friction element has a rotation center A friction surface formed on at least one of the two inertial disks so that a radial distance from the circumferential direction changes in the circumferential direction, and is provided movably in a radial direction on the other inertial disk, And a spring which is always in sliding contact with the friction surface. A movable member resiliently biased by means, and opposing the exclusion chamber and the movable member in response to a radial movement of the movable member in accordance with a change in a relative rotation angle between the two inertial disks. A two-mass flywheel for a clutch device, wherein the function of the piston element is assigned to the movable member by changing the gap size between the surfaces.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3806013A DE3806013A1 (en) | 1988-02-26 | 1988-02-26 | Clutch for changing operating conditions, in particular a two-mass flywheel |
| DE3806013.2 | 1988-02-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01255738A JPH01255738A (en) | 1989-10-12 |
| JP2703977B2 true JP2703977B2 (en) | 1998-01-26 |
Family
ID=6348206
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1043349A Expired - Lifetime JP2703977B2 (en) | 1988-02-26 | 1989-02-27 | 2 mass flywheel for clutch device |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2703977B2 (en) |
| DE (1) | DE3806013A1 (en) |
| FR (1) | FR2630512B1 (en) |
| IT (1) | IT1232594B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0645728Y2 (en) * | 1989-12-22 | 1994-11-24 | 株式会社大金製作所 | Liquid viscosity damper |
| JPH0756318B2 (en) * | 1990-10-29 | 1995-06-14 | 株式会社大金製作所 | Liquid viscosity damper |
| JPH06147273A (en) * | 1992-11-02 | 1994-05-27 | Aisin Seiki Co Ltd | Torque fluctuation absorbing device |
| US6416416B1 (en) | 1997-10-29 | 2002-07-09 | Rohs-Voigt Patentverwertungsgesellschaft Mbh | Torsional vibration damper with drag element |
| DE19817907A1 (en) | 1998-04-22 | 1999-10-28 | Rohs Voigt Patentverwertungsge | Friction disc damper |
| EP1812728B1 (en) * | 2004-11-13 | 2014-09-10 | Schaeffler Technologies GmbH & Co. KG | Torque transmission device |
| DE102010009218A1 (en) * | 2010-02-25 | 2011-08-25 | GM Global Technology Operations LLC, ( n. d. Ges. d. Staates Delaware ), Mich. | Damping device for e.g. gear change in gear box in drive train of motor vehicle, has friction linings for forming frictional contact between gear wheel and shaft that are releasably engageable by friction linings based on parameters |
| CN103398140B (en) * | 2013-08-06 | 2015-07-22 | 浙江锦豪电器有限公司 | Adjustable damping device |
| DE102017223450B4 (en) | 2017-12-20 | 2019-12-12 | Audi Ag | centrifugal pendulum |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2361574A1 (en) * | 1976-08-09 | 1978-03-10 | Ferodo Sa | Friction clutch for automobile - has friction pads to inhibit large torsional oscillations by hysteresis |
| FR2381206A1 (en) * | 1977-02-22 | 1978-09-15 | Ferodo Sa | Vehicle clutch plate with resiliently connected discs - has friction element under leaf spring pressure to damp relative torsional vibration of discs |
| FR2398927A1 (en) * | 1977-07-27 | 1979-02-23 | Stichler Bernd | Main clutch assembly for motor vehicle - has different stiffness damping springs and multiple slotted pads on pressure plate |
| DE2848748C3 (en) * | 1978-11-10 | 1981-03-26 | J.M. Voith Gmbh, 89522 Heidenheim | Elastic coupling in disc design |
| DE3418671C2 (en) * | 1983-10-24 | 1996-05-23 | Luk Lamellen & Kupplungsbau | Damping device for absorbing or compensating for rotary shocks |
| DE3447926C2 (en) * | 1983-11-15 | 1995-07-06 | Luk Lamellen & Kupplungsbau | Device for compensating torsional shocks |
| JPS61161449U (en) * | 1985-03-29 | 1986-10-06 | ||
| DE3610735A1 (en) * | 1985-04-04 | 1986-10-09 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | DEVICE WITH AT LEAST TWO RELATIVELY TURNING FLYING EQUIPMENT PROVIDED DAMPING DEVICE AND SLIP CLUTCH |
| DE3645392B4 (en) * | 1985-09-07 | 2009-11-26 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Anti-rotation device |
-
1988
- 1988-02-26 DE DE3806013A patent/DE3806013A1/en active Granted
-
1989
- 1989-02-17 IT IT8967100A patent/IT1232594B/en active
- 1989-02-27 FR FR8902934A patent/FR2630512B1/en not_active Expired - Fee Related
- 1989-02-27 JP JP1043349A patent/JP2703977B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| IT8967100A0 (en) | 1989-02-17 |
| IT1232594B (en) | 1992-02-26 |
| DE3806013A1 (en) | 1989-09-07 |
| FR2630512A1 (en) | 1989-10-27 |
| DE3806013C2 (en) | 1989-12-07 |
| JPH01255738A (en) | 1989-10-12 |
| FR2630512B1 (en) | 1994-05-27 |
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