JPH09166180A - Two-inlet type flywheel - Google Patents
Two-inlet type flywheelInfo
- Publication number
- JPH09166180A JPH09166180A JP32583795A JP32583795A JPH09166180A JP H09166180 A JPH09166180 A JP H09166180A JP 32583795 A JP32583795 A JP 32583795A JP 32583795 A JP32583795 A JP 32583795A JP H09166180 A JPH09166180 A JP H09166180A
- Authority
- JP
- Japan
- Prior art keywords
- friction
- flywheel
- spring
- seat
- ring
- 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.)
- Granted
Links
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、摩擦式振動減衰装
置を有する2マス型フライホイールに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a two-mass type flywheel having a friction type vibration damping device.
【0002】[0002]
【従来の技術】従来の2マス型フライホイールの摩擦式
振動減衰装置としては、例えば実公平6-2054号公報に示
されるものがある。このものは、二つのフライホイール
の間に介設されるもので、図7に示すように一対の駆動
板a1,a2から被動板bに回転を伝達するものにおい
て、被動板bのスラスト部b1の両面にライニングcを
設け、一方のライニングc側にスラスト板dを当てて皿
バネeで加圧し、スラスト部b1にスラスト板dと駆動
板a2を摩擦的に連結させている。この従来装置におい
て、スラスト板dは、皿バネeの圧力をライニングc及
びスラスト部b1に伝えるために必要であり、これがな
ければ線接触をする皿バネeとの接触面においてかじり
が生じるおそれがある。また、この皿バネは大径である
ため高価である。2. Description of the Related Art As a conventional friction type vibration damping device for a two-mass type flywheel, there is one disclosed in Japanese Utility Model Publication No. 6-2054. This is provided between two flywheels, and as shown in FIG. 7, in the case where the rotation is transmitted from the pair of drive plates a 1 and a 2 to the driven plate b, the thrust of the driven plate b is A lining c is provided on both sides of the part b 1 , and a thrust plate d is applied to one side of the lining c and pressure is applied by a disc spring e to frictionally connect the thrust plate d and the drive plate a 2 to the thrust part b 1. There is. In this conventional device, the thrust plate d is necessary for transmitting the pressure of the disc spring e to the lining c and the thrust portion b 1 , and if this is not the case, galling may occur at the contact surface with the disc spring e that makes a line contact. There is. Further, this disc spring has a large diameter and is expensive.
【0003】[0003]
【発明が解決しようとする課題】本発明は、2マス型フ
ライホイールにおける摩擦式振動減衰装置の部分を、バ
ネとの接触面にかじりが生じることなく、しかも部品点
数が少なく安価に作ることができる部材を得ることを課
題とする。SUMMARY OF THE INVENTION According to the present invention, the frictional vibration damping device portion of a two-mass flywheel can be manufactured inexpensively with no galling on the contact surface with the spring and with a small number of parts. An object is to obtain a member that can be used.
【0004】[0004]
【課題を解決するための手段】前記課題を達成するする
ための手段の一つは、請求項1に記載したとおり、第1
フライホイールの内面に摩擦式振動減衰装置を設け、該
摩擦式振動減衰装置の摩擦駆動板と第2フライホイール
の間に緩衝バネを介設した2マス型フライホイールにお
いて、前記摩擦式振動減衰装置は、第1フライホイール
の内面の摩擦面と、該摩擦面に順次重なる摩擦板、摩擦
駆動板、座付リングバネ及び押し板を備え、該座付リン
グバネは、一巻き未満の平坦なリング座部と、巻き方向
に波状に湾曲した略1巻きのリングバネ部とからなるこ
とを特徴とする。[Means for Solving the Problems] One of the means for achieving the above object is as described in claim 1,
In a two-mass type flywheel in which a friction type vibration damping device is provided on an inner surface of a flywheel, and a buffer spring is interposed between a friction drive plate of the friction type vibration damping device and a second flywheel, the friction type vibration damping device. Includes a friction surface on the inner surface of the first flywheel, and a friction plate, a friction drive plate, a seat ring spring and a push plate that sequentially overlap the friction surface, and the seat ring spring has a flat ring seat portion of less than one turn. And a ring spring part of approximately one turn that is curved in a wavy shape in the winding direction.
【0005】[0005]
【発明の実施の形態】以下、図面を参照して本発明の実
施の形態を説明する。図1は本発明を実施した2マス型
フライホイールであり、該2マス型フライホイール1
は、第1フライホイール2と第2フライホイール3を有
し、第1フライホイール2はボス4に軸受5を介して支
持され、第2フライホイール3は、ボス4に固着され
る。そして、第1フライホイール2と第2フライホール
3の間には、摩擦式振動減衰装置6と強弱2種の緩衝バ
ネ7が介設されている。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a two-mass type flywheel 1 according to the present invention.
Has a first flywheel 2 and a second flywheel 3, the first flywheel 2 is supported by a boss 4 via bearings 5, and the second flywheel 3 is fixed to the boss 4. A friction type vibration damping device 6 and two types of buffer springs 7 having strength and weakness are provided between the first flywheel 2 and the second flyhole 3.
【0006】また、第1フライホイール2には図外のエ
ンジンのクランク軸に固定された駆動板21、リングギ
ヤ22、バネ保持板23等が固着されている。ボス4には
被動板41が固着されて緩衝バネ7から伝わるトルクを
ボス4に伝え、更にスプライン42に嵌合する図外のミ
ッションの入力軸に伝える。A drive plate 2 1 , a ring gear 2 2 , a spring holding plate 2 3 and the like, which are fixed to the crankshaft of the engine (not shown), are fixed to the first flywheel 2. The driven plate 4 1 is fixed to the boss 4, and the torque transmitted from the buffer spring 7 is transmitted to the boss 4 and further transmitted to the input shaft of a transmission (not shown) fitted to the spline 4 2 .
【0007】前記摩擦式振動減衰装置6は、図1,2に
示すように第1フライホイール2を構成の一部としてこ
れに組付けられる。該第1フライホイール2の内周側の
内面には、平らな摩擦面8、逃げ溝9、筒部10及び内
周部11が設けられ、該筒部10にプラスチック材から
なる摩擦板12、鋼製の摩擦駆動板13、座付きリング
バネ14が順次嵌められ、該座付きリングバネ14を加
圧する状態で押し板15が重ねられ、該押し板15はリ
ベット16で内周部11に固定される。As shown in FIGS. 1 and 2, the friction type vibration damping device 6 has a first flywheel 2 incorporated therein as a part of its construction. The inner surface of the first flywheel 2 on the inner peripheral side is provided with a flat friction surface 8, a clearance groove 9, a cylindrical portion 10 and an inner peripheral portion 11, and the cylindrical portion 10 has a friction plate 12 made of a plastic material, A friction drive plate 13 made of steel and a ring spring 14 with a seat are sequentially fitted, and a pressing plate 15 is superposed in a state of pressing the ring spring 14 with a seat, and the pressing plate 15 is fixed to the inner peripheral portion 11 by a rivet 16.
【0008】図3,4は座付きリングバネ14を示し、
該座付きリングバネ14は、薄板が螺旋状に約1.75
周だけ巻かれたもので、リング座部17とリングバネ部
18からなり、これを展開すれば図5に示すように一連
のものとして形成されている。3 and 4 show a ring spring 14 with a seat,
The seated ring spring 14 is a thin plate spirally shaped about 1.75.
It is wound only around the circumference, and is composed of a ring seat portion 17 and a ring spring portion 18, and when it is expanded, it is formed as a series as shown in FIG.
【0009】リング座部17は、平坦で始端171から
図3で反時計方向に終端172までの約0.75巻きの
範囲であり、リングバネ部18は、波形に高さを変化さ
せたもので、前記終端172を始端として、4個の山部
181と谷部182を交互に形成して終端183に至る約
1巻きの範囲であり、自由状態で各谷部182がリング
座部17に接触する。The ring seat portion 17 is flat and has a range of about 0.75 turns from the start end 17 1 to the end end 17 2 in the counterclockwise direction in FIG. 3, and the ring spring portion 18 changes its height in a wave shape. With the end 17 2 being the starting end, four peaks 18 1 and troughs 18 2 are alternately formed to reach the end 18 3 in a range of about 1 turn, and each trough 18 2 in the free state. Contacts the ring seat 17.
【0010】座付きリングバネ14の各部の寸法は、例
えば直径D=112mm、板幅W=8mm、板厚T=
1.8mm、山の高さH=3mmとされ、コイル状のシ
リコンクローム鋼を圧延して切断し、所定部分を波形に
変形させて、熱処理することにより作られ、相手側の押
し板15は窒化処理された鋼板で作られる。The dimensions of each part of the seated ring spring 14 are, for example, diameter D = 112 mm, plate width W = 8 mm, and plate thickness T =.
The height of the ridge is 1.8 mm and the height H is 3 mm. The coil-shaped silicon chrome steel is rolled and cut, and a predetermined portion is deformed into a corrugated shape and heat-treated. Made of nitriding steel plate.
【0011】座付きリングバネ14は、リング座部17
を摩擦駆動板13に接触させ、リングバネ部18が押し
板15に押されて山部181を僅かに圧縮した状態で保
持される。The seated ring spring 14 has a ring seat portion 17
Is brought into contact with the friction drive plate 13, and the ring spring portion 18 is pushed by the push plate 15 to hold the mountain portion 18 1 in a slightly compressed state.
【0012】そして、エンジンから第1フライホイール
2に振動回転が伝達されると、摩擦式振動減衰装置6で
振動の一部を吸収しながらトルクを第1フライホイール
2から摩擦駆動板13に伝える。この場合、該装置6の
各接触部のうち、摩擦面8と摩擦板12、該摩擦板12
と摩擦駆動板13、リングバネ部18と押し板15の間
は互いに摺動し、該摺動によって振動エネルギを吸収す
る。When the oscillating rotation is transmitted from the engine to the first flywheel 2, the friction type vibration damping device 6 absorbs a part of the vibration and transmits the torque from the first flywheel 2 to the friction drive plate 13. . In this case, among the respective contact portions of the device 6, the friction surface 8 and the friction plate 12, the friction plate 12
The friction drive plate 13, the ring spring portion 18, and the pressing plate 15 slide against each other, and the sliding energy absorbs vibration energy.
【0013】図6は、4種の仕様で作られた本発明の座
付きリングバネ14と従来の皿バネとを用いて実験した
場合の、バネ部分のセット高さと摩擦トルクの関係を示
すもので、横軸にセット高さの設計値と製品のセット高
さとの差mmをとり、縦軸に実測した摩擦トルクkgf
・mをとると、皿バネは、幅に比して直径が大径である
ため、弾発力の変化が少なく、曲線Aに示されるように
略一定の所定の摩擦トルクを発生するが、座付きリング
バネ14にあっては、仕様によって曲線〜のように
変化し、セット高さが設計値より低いと摩擦トルクが急
増する。しかし、セット高さが高い場合の変化は少な
く、0〜+0.5mmの範囲では摩擦トルクの差は少な
いので実用上差支えがない。FIG. 6 shows the relationship between the set height of the spring portion and the friction torque when an experiment was carried out using the ring spring with seat 14 of the present invention made in four types of specifications and the conventional disc spring. The horizontal axis shows the difference mm between the design value of the set height and the set height of the product, and the vertical axis shows the measured friction torque kgf.
When m is taken, the disc spring has a large diameter compared to the width, so that the elastic force changes little and generates a substantially constant predetermined friction torque as shown by the curve A. In the seated ring spring 14, the curve changes depending on the specifications, and when the set height is lower than the design value, the friction torque increases sharply. However, there is little change when the set height is high, and there is little difference in friction torque in the range of 0 to +0.5 mm, so there is no practical problem.
【0014】なお、前記実施例においてリングバネ部1
8に山部181を4個設けたものを示したが、3〜9個
など3個以上の任意の数を設けることができ、リング座
部17の円に対する比率を前記の0.75より大にして
1に近づけてもよい。In the above embodiment, the ring spring portion 1
8 has four ridges 18 1 provided, but any number of 3 or more such as 3 to 9 can be provided, and the ratio of the ring seat 17 to the circle is 0.75 or more. It may be close to 1 in a large amount.
【0015】[0015]
【発明の効果】請求項1の発明によれば、摩擦式振動減
衰装置における座付きリングバネは、リング座部が広い
面接触をし、リングバネ部が複数の山部で面接触するの
で、接触面にカジリが生じるのが防止され、またリング
座部とリングバネ部を一体としたから、2マス型フライ
ホイールの部品数を減少させることができ、しかもリン
グバネ部を巻き方向に波状に湾曲させることにより形成
したから、皿バネの如き高価な部品を用いることなく充
分な弾発力とこれに伴う摩擦トルクを生じさせることが
できる効果がある。According to the first aspect of the invention, in the ring spring with a seat in the friction type vibration damping device, the ring seat portion makes wide surface contact, and the ring spring portion makes surface contact at the plurality of peak portions, so that the contact surface is It is possible to reduce the number of parts of the two-mass type flywheel because the ring seat is integrated with the ring spring part, and the ring spring part is formed by curving the ring spring part in a wavy shape. Therefore, there is an effect that a sufficient elastic force and a friction torque associated therewith can be generated without using an expensive component such as a disc spring.
【図1】 本発明を実施した2マス型のフライホイール
の断面図FIG. 1 is a sectional view of a two-mass type flywheel embodying the present invention.
【図2】 同上要部の断面図FIG. 2 is a sectional view of a main part of the same as above.
【図3】 本発明の座付きリングバネの斜視図FIG. 3 is a perspective view of a ring spring with a seat according to the present invention.
【図4】 同上側面図FIG. 4 is a side view of the same.
【図5】 同上展開図[Figure 5] Same as above
【図6】 摩擦トルクとセット高さの関連図[Fig. 6] Relationship between friction torque and set height
【図7】 従来例の断面図FIG. 7 is a sectional view of a conventional example.
2 第1フライホイール 3 第2フライホ
イール 6 摩擦式振動減衰装置 7 緩衝バネ 8 摩擦面 12 摩擦板 14 座付きリングバネ 15 押し板 17 リング座部 18 リングバネ
部 181 山部 182 谷部2 1st flywheel 3 2nd flywheel 6 Friction type vibration damping device 7 Buffer spring 8 Friction surface 12 Friction plate 14 Ring spring with seat 15 Push plate 17 Ring seat part 18 Ring spring part 18 1 Mountain part 18 2 Valley part
Claims (1)
減衰装置を設け、該摩擦式振動減衰装置の摩擦駆動板と
第2フライホイールの間に緩衝バネを介設した2マス型
フライホイールにおいて、前記摩擦式振動減衰装置は、
第1フライホイールの内面の摩擦面と、該摩擦面に順次
重なる摩擦板、摩擦駆動板、座付リングバネ及び押し板
を備え、該座付リングバネは、一巻き未満の平坦なリン
グ座部と、巻き方向に波状に湾曲した略1巻きのリング
バネ部とからなることを特徴とする2マス型フライホイ
ール。1. A two-mass type flywheel in which a friction type vibration damping device is provided on the inner surface of a first flywheel, and a buffer spring is interposed between a friction drive plate of the friction type vibration damping device and a second flywheel. The friction type vibration damping device,
A friction surface on the inner surface of the first flywheel, and a friction plate, a friction drive plate, a ring spring with a seat, and a push plate that sequentially overlap with the friction surface, the ring spring with a seat having a flat ring seat portion of less than one turn; A two-mass type flywheel, characterized in that it comprises a ring spring part of approximately one turn that is curved in a wavy shape in the winding direction.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32583795A JP3773572B2 (en) | 1995-12-14 | 1995-12-14 | 2-mass type flywheel |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32583795A JP3773572B2 (en) | 1995-12-14 | 1995-12-14 | 2-mass type flywheel |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH09166180A true JPH09166180A (en) | 1997-06-24 |
JP3773572B2 JP3773572B2 (en) | 2006-05-10 |
Family
ID=18181173
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP32583795A Expired - Fee Related JP3773572B2 (en) | 1995-12-14 | 1995-12-14 | 2-mass type flywheel |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3773572B2 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002526731A (en) * | 1998-10-07 | 2002-08-20 | ヴァレオ | Dual mass member damping flywheel, especially for automobiles |
EP1451483B1 (en) * | 2001-11-23 | 2006-05-24 | Volkswagen Aktiengesellschaft | Dual mass flywheel |
JP2011208750A (en) * | 2010-03-30 | 2011-10-20 | Yutaka Giken Co Ltd | Engine flywheel device and method for manufacturing the same |
JP2016008712A (en) * | 2014-06-26 | 2016-01-18 | アイシン精機株式会社 | Damper device |
CN111692283A (en) * | 2019-03-15 | 2020-09-22 | 株式会社艾科赛迪 | Damping device |
-
1995
- 1995-12-14 JP JP32583795A patent/JP3773572B2/en not_active Expired - Fee Related
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002526731A (en) * | 1998-10-07 | 2002-08-20 | ヴァレオ | Dual mass member damping flywheel, especially for automobiles |
EP1451483B1 (en) * | 2001-11-23 | 2006-05-24 | Volkswagen Aktiengesellschaft | Dual mass flywheel |
US7082855B2 (en) | 2001-11-23 | 2006-08-01 | Volkswagen Aktiengesellschaft | Dual-mass flywheel |
CN100380019C (en) * | 2001-11-23 | 2008-04-09 | 大众汽车有限公司 | Dual-mass flywheel |
JP2011208750A (en) * | 2010-03-30 | 2011-10-20 | Yutaka Giken Co Ltd | Engine flywheel device and method for manufacturing the same |
JP2016008712A (en) * | 2014-06-26 | 2016-01-18 | アイシン精機株式会社 | Damper device |
CN111692283A (en) * | 2019-03-15 | 2020-09-22 | 株式会社艾科赛迪 | Damping device |
US11619282B2 (en) | 2019-03-15 | 2023-04-04 | Exedy Corporation | Damper device |
Also Published As
Publication number | Publication date |
---|---|
JP3773572B2 (en) | 2006-05-10 |
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