JPH0571588A - Flywheel - Google Patents
FlywheelInfo
- Publication number
- JPH0571588A JPH0571588A JP23452291A JP23452291A JPH0571588A JP H0571588 A JPH0571588 A JP H0571588A JP 23452291 A JP23452291 A JP 23452291A JP 23452291 A JP23452291 A JP 23452291A JP H0571588 A JPH0571588 A JP H0571588A
- Authority
- JP
- Japan
- Prior art keywords
- mass body
- crankshaft
- spring member
- flywheel
- mass
- 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.)
- Pending
Links
Landscapes
- Mechanical Operated Clutches (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はクランクシャフトの端部
に取り付けられるフライホイールに関する。FIELD OF THE INVENTION The present invention relates to a flywheel mounted on the end of a crankshaft.
【０００２】[0002]
【従来の技術】この種のフライホイールは、エンジンの
トルク変動に伴うクランクシャフトの回転変動を少なく
すると共に、クランクシャフトの捩り振動を低減し、ク
ラッチを介して出力軸に円滑に動力伝達できるように様
々な工夫が施されている。2. Description of the Related Art This type of flywheel reduces fluctuations in crankshaft rotation due to fluctuations in engine torque, reduces torsional vibrations in the crankshaft, and enables smooth power transmission to an output shaft via a clutch. Has been devised in various ways.
【０００３】このようなフライホイールのうちで、図４
〜図５に示すものは、クランクシャフト１に固定した質
量体３０に別の質量体３１を相対回動できるように組み
付け、これら質量体３０，３１をばね部材３２で回動方
向に弾性的に連繋すると共に、これら質量体３０，３１
間に転動体３３を介装することにより、両質量体３０，
３１の相対回動時にばね部材３２の緩衝機能と転動体３
３の減衰機能を発揮させ、クランクシャフト１の捩り振
動を低減するようになっている（特公昭５７−５５９３
７号公報参照）。Among such flywheels, FIG.
5 shows that another mass body 31 is assembled to the mass body 30 fixed to the crankshaft 1 so as to be relatively rotatable, and these mass bodies 30 and 31 are elastically moved in the rotation direction by the spring member 32. These mass bodies 30 and 31 are connected to each other.
By interposing the rolling element 33 between the two mass bodies 30,
The cushioning function of the spring member 32 and the rolling element 3 at the time of relative rotation of 31.
The damping function of No. 3 is exhibited to reduce the torsional vibration of the crankshaft 1 (Japanese Patent Publication No. 57-5593).
No. 7).
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、近年の
自動車の高級化に伴い、自動車の低速走行時から高速走
行時まで動力伝達系の捩り振動をより一層効果的に抑制
し得るフライホイールの提供が望まれていた。However, with the recent advancement of automobiles, it is possible to provide a flywheel that can more effectively suppress the torsional vibration of the power transmission system during low-speed traveling to high-speed traveling of the automobile. Was wanted.
【０００５】本発明は上記要望に応えるために案出され
たものである。The present invention has been devised to meet the above demand.
【０００６】[0006]
【課題を解決するための手段】即ち本発明は、クランク
シャフトに固定した第１質量体に高剛性のばね部材を介
して第２質量体を所定角度相対回動できるように連繋
し、この第２質量体に低剛性のばね部材を介して第３質
量体を所定角度相対回動できるように連繋してある。That is, according to the present invention, a first mass body fixed to a crankshaft is connected to a second mass body through a highly rigid spring member so as to be relatively rotatable by a predetermined angle. The third mass body is connected to the two mass bodies via a low-rigidity spring member so as to be relatively rotatable by a predetermined angle.
【０００７】[0007]
【作用】フライホイールへの入力トルクが小さな場合
（エンジンの低回転域の場合）には、低剛性のばね部材
のみが作用し、第１質量体と第２質量体がクランクシャ
フトとともに一体回動して、クランクシャフトに第１質
量体及び第２質量体の慣性モーメントが作用する。When the input torque to the flywheel is small (in the low engine speed range), only the low-rigidity spring member acts and the first mass body and the second mass body rotate together with the crankshaft. Then, the moments of inertia of the first mass body and the second mass body act on the crankshaft.
【０００８】フライホイールへの入力トルクが大きな場
合（エンジンの高回動域の場合）には、低剛性のばね部
材が第２質量体と第３質量体とにより押し縮められて密
着し、低剛性のばね部材に代わって高剛性のばね部材が
作用する。従って、第１質量体がクランクシャフトと一
体回動し、クランクシャフトに第１質量体の慣性モーメ
ントが作用する。When the input torque to the flywheel is large (in the high rotation range of the engine), the low-rigidity spring member is pressed and contracted by the second mass body and the third mass body to be in close contact with each other. A highly rigid spring member acts instead of the rigid spring member. Therefore, the first mass body rotates integrally with the crankshaft, and the moment of inertia of the first mass body acts on the crankshaft.
【０００９】[0009]
【実施例】以下本発明の実施例を図面に基づき詳述す
る。Embodiments of the present invention will now be described in detail with reference to the drawings.
【００１０】図１は中心線から下半分を省略して示す本
実施例のフライホイールの断面図であり、この図におい
て１はクランクシャフトである。FIG. 1 is a cross-sectional view of the flywheel of this embodiment shown by omitting the lower half from the center line. In this figure, 1 is a crankshaft.
【００１１】このクランクシャフト１の軸端には第１質
量体２をボルト３で固定してある。第１質量体２は、ク
ランクシャフト１に固定する取付基部２ａと、この取付
基部２ａの外周側に形成した円筒部２ｂと、この円筒部
２ｂよりも外周方向へ延出する略円板状のプレート部２
ｃとから成っている。A first mass body 2 is fixed to a shaft end of the crankshaft 1 with bolts 3. The first mass body 2 has a mounting base portion 2a fixed to the crankshaft 1, a cylindrical portion 2b formed on the outer peripheral side of the mounting base portion 2a, and a substantially disc-like shape extending outward from the cylindrical portion 2b. Plate part 2
It consists of c and.
【００１２】そして、この第１質量体２の円筒部２ｂに
は第３質量体４を軸受５を介して相対回動できるように
組み付けてある。第３質量体４は、第１質量体２のプレ
ート部２ｃに対して所定の間隔をもって対峙する略円板
状のプレート部４ａと、第１質量体２のプレート部２ｃ
側へ延出する円筒部４ｂとからなっており、前記プレー
ト部４ａの内側側面４ｃには略円板状の出力部材６をリ
ベット７で固定してある。A third mass body 4 is attached to the cylindrical portion 2b of the first mass body 2 via a bearing 5 so as to be relatively rotatable. The third mass body 4 has a substantially disk-shaped plate portion 4a facing the plate portion 2c of the first mass body 2 at a predetermined interval, and the plate portion 2c of the first mass body 2.
A cylindrical portion 4b extending to the side, and a substantially disk-shaped output member 6 is fixed to the inner side surface 4c of the plate portion 4a with a rivet 7.
【００１３】そして、この第３質量体４には、その円筒
部４ｂに略円板状の第２質量体８を軸受９を介して相対
回動できるように組み付けてある。第２質量体８は、第
１質量体２のプレート部２ｃと第３質量体４のプレート
部４ａとの間に所定の間隔をもって位置するプレート部
８ａと、その外周側に形成した円筒部８ｂとからなり、
その円筒部８ｂには図外のスタータモータのピニオンギ
ヤに噛合するリングギヤ１０を固定してある。Then, a substantially disk-shaped second mass body 8 is attached to the cylindrical portion 4b of the third mass body 4 so as to be relatively rotatable via a bearing 9. The second mass body 8 includes a plate portion 8a located at a predetermined interval between the plate portion 2c of the first mass body 2 and the plate portion 4a of the third mass body 4, and a cylindrical portion 8b formed on the outer peripheral side thereof. And consists of
A ring gear 10 meshing with a pinion gear of a starter motor (not shown) is fixed to the cylindrical portion 8b.
【００１４】そして、この第２質量体８のプレート部８
ａ，第３質量体４のプレート部４ａ及び出力部材６の円
周方向の相対応する位置に複数のばね受容部１１，１
２，１３を形成してあり、このばね受容部１１，１２，
１３に低剛性のばね部材（例えば圧縮コイルスプリン
グ）１４を所定量押し縮めた状態で収容してある。これ
により、第２質量体８と第３質量体４は、低剛性のばね
部材１４を介して回動方向に弾性的に連繋されることと
なる。The plate portion 8 of the second mass body 8
a, a plurality of spring receiving portions 11, 1 at corresponding positions in the circumferential direction of the plate portion 4a of the third mass body 4 and the output member 6.
2 and 13 are formed, and these spring receiving portions 11 and 12,
A low-rigidity spring member (for example, a compression coil spring) 14 is housed in 13 while compressed by a predetermined amount. As a result, the second mass body 8 and the third mass body 4 are elastically connected to each other in the rotation direction via the spring member 14 having a low rigidity.
【００１５】又、この第２質量体８のプレート部８ａの
第１質量体側側面１５には出力部材１６をリベット１７
で固定してある。そして、この第２質量体８のプレート
部８ａ，出力部材１６及び第１質量体２のプレート部２
ｃの円周方向の相対応する位置にばね受容部１８，１
９，２０を形成してあり、このばね受容部１８，１９，
２０内に高剛性のばね部材２１を所定量押し縮めた状態
で収容してある。これにより、第１質量体２と第２質量
体８は、高剛性のばね部材２１を介して回動方向に弾性
的に連繋されることとなる。Further, an output member 16 is provided with a rivet 17 on the side surface 15 of the plate portion 8a of the second mass body 8 on the first mass body side.
It is fixed at. Then, the plate portion 8a of the second mass body 8, the output member 16, and the plate portion 2 of the first mass body 2
At the corresponding positions in the circumferential direction of c, the spring receiving portions 18, 1
9 and 20 are formed, and these spring receiving portions 18, 19,
A high-rigidity spring member 21 is accommodated in the unit 20 while being compressed by a predetermined amount. As a result, the first mass body 2 and the second mass body 8 are elastically connected to each other in the rotation direction via the highly rigid spring member 21.
【００１６】尚、第１質量体２の慣性モーメント
（Ｉ1）と第２質量体８の慣性モーメント（Ｉ2）の和
（Ｉ1＋Ｉ2）は第３質量体４の慣性モーメント（Ｉ3）
よりも大きく（Ｉ1＋Ｉ2＞Ｉ3）、第２質量体８の慣性
モーメントと第３質量体４の慣性モーメントの和は第１
質量体２の慣性モーメントよりも大きく（Ｉ2＋Ｉ3＞Ｉ
1）なるように各質量体２，４，８を形成してある。The sum of the inertia moment (I 1 ) of the first mass body 2 and the moment of inertia (I 2 ) of the second mass body 8 (I 1 + I 2 ) is the moment of inertia of the third mass body 4 (I 3). )
(I 1 + I 2 > I 3 ), the sum of the moment of inertia of the second mass body 8 and the moment of inertia of the third mass body 4 is the first
Greater than the moment of inertia of the mass body 2 (I 2 + I 3 > I
The mass bodies 2, 4, and 8 are formed so as to be 1 ).
【００１７】２２はクラッチディスクであり、このクラ
ッチディスク２２が第３質量体４の外側側面４ｄに摩擦
係合する。２３はクラッチディスク２２とスプライン嵌
合する出力軸である。Reference numeral 22 denotes a clutch disc, which is frictionally engaged with the outer side surface 4d of the third mass body 4. An output shaft 23 is spline-fitted with the clutch disc 22.
【００１８】以上の実施例構造によれば、エンジン（図
示せず）の低回転域の場合、フライホイールＡへの入力
トルクが小さいため、低剛性のばね部材１４のみが作用
してトルク変動に伴う衝撃を吸収する。この際、図２の
（Ａ系）に示すように、第１質量体２及び第２質量体８
がクランクシャフト１とともに回動する一方、第３質量
体４が出力軸２３とともに回動するクラッチディスク２
２に摩擦係合し、第２質量体８と第３質量体４との間で
相対回動が生ずることとなる。従って、クランクシャフ
ト１には第１質量体２及び第２質量体８の慣性モーメン
ト（Ｉ1＋Ｉ2）が作用する一方、出力軸２３側には第３
質量体４の慣性モーメント（Ｉ3）のみが作用すること
となる。According to the structure of the above-described embodiment, in the low rotation range of the engine (not shown), since the input torque to the flywheel A is small, only the low-rigidity spring member 14 acts to reduce the torque fluctuation. Absorb the accompanying shock. At this time, as shown in (A system) of FIG. 2, the first mass body 2 and the second mass body 8
The clutch disk 2 in which the third mass body 4 rotates together with the output shaft 23 while the third mass body 4 rotates together with the crankshaft 1.
2 will be frictionally engaged and relative rotation will occur between the second mass body 8 and the third mass body 4. Therefore, the moment of inertia (I 1 + I 2 ) of the first mass body 2 and the second mass body 8 acts on the crankshaft 1, while the third moment is exerted on the output shaft 23 side.
Only the moment of inertia (I 3 ) of the mass body 4 acts.
【００１９】エンジンの高回転域の場合、フライホイー
ルＡへの入力トルクが大きくなるため、第２質量体８と
第３質量体４を連繋する低剛性のばね部材１４は、両者
４，８に押し縮められて密着し、ばね作用を発揮しな
い。この際、図２の（Ｂ系）に示すように、第２質量体
８及び第３質量体４がクラッチディスク２２を介して出
力軸２３に一体化する一方、第１質量体２と第２質量体
８とを連繋する高剛性のばね部材２１が低剛性のばね部
材１４に代わって作用し、第１質量体２と第２質量体８
との間で相対回動が生ずることとなる。従って、クラン
クシャフト１には第１質量体２の慣性モーメント
（Ｉ1）のみが作用し、出力軸には第２質量体８及び第
３質量体４の慣性モーメント（Ｉ2＋Ｉ3）が作用するこ
ととなる。In the high engine speed range, the input torque to the flywheel A becomes large, so that the low-rigidity spring member 14 connecting the second mass body 8 and the third mass body 4 is connected to the both 4 and 8. It is compressed and comes into close contact, and does not exert a spring effect. At this time, as shown in (B system) of FIG. 2, while the second mass body 8 and the third mass body 4 are integrated with the output shaft 23 via the clutch disc 22, the first mass body 2 and the second mass body 2 The high-rigidity spring member 21 that connects the mass body 8 acts instead of the low-rigidity spring member 14, and the first mass body 2 and the second mass body 8 are connected.
Relative rotation will occur between and. Therefore, only the moment of inertia (I 1 ) of the first mass body 2 acts on the crankshaft 1, and the moment of inertia (I 2 + I 3 ) of the second mass body 8 and the third mass body 4 acts on the output shaft. Will be done.
【００２０】以上のように本実施例は、エンジン始動時
には、第１質量体２及び第２質量体８の大きな慣性モー
メント（Ｉ1＋Ｉ2）をクランクシャフト１に作用させ
て、円滑かつ確実にエンジンを始動させることができ
る。又、本実施例は、エンジンの低速回転域と高速回転
域とで、クランクシャフト１側と出力軸２３側とに作用
する慣性モーメントの割合を変えると共に、作用するば
ね部材の剛性をも変えるようにしてあるため、エンジン
の低速回転域から高速回転域に至る広範囲のエンジン回
転域において、クランクシャフト１及び出力軸２３を含
めた動力伝達系の捩り振動を従来例よりも効果的に低減
でき、捩り振動に起因する異音の発生をより一層抑制す
ることが可能となる。As described above, in this embodiment, when the engine is started, the large inertia moments (I 1 + I 2 ) of the first mass body 2 and the second mass body 8 act on the crankshaft 1 to ensure smooth and reliable operation. The engine can be started. Further, in this embodiment, the ratio of the moment of inertia acting on the crankshaft 1 side and the output shaft 23 side is changed between the low speed rotation range and the high speed rotation range of the engine, and the rigidity of the acting spring member is also changed. Therefore, the torsional vibration of the power transmission system including the crankshaft 1 and the output shaft 23 can be effectively reduced as compared with the conventional example in a wide range of engine rotation range from the low speed rotation range to the high speed rotation range of the engine. It is possible to further suppress the generation of abnormal noise due to torsional vibration.
【００２１】図３は本発明の他の実施例を示すものであ
る。即ち、本実施例は、前記実施例で示した第２質量体
８と第３質量体４の間に粘性減衰力発生部２４を形成し
たものであり、第２質量体８と第３質量体４とが相対回
動した際に、粘性減衰力発生部２４が粘性抵抗力を発生
し、その粘性減衰力発生部２４が低剛性のばね部材１４
と協働して捩り振動を吸収・減衰する。この実施例によ
れば、クランクシャフト１及び出力軸２３を含めた動力
伝達系の捩り振動を前記実施例よりも一層効果的に低減
することができる。FIG. 3 shows another embodiment of the present invention. That is, in this embodiment, the viscous damping force generating portion 24 is formed between the second mass body 8 and the third mass body 4 shown in the above-mentioned embodiment, and the second mass body 8 and the third mass body 4 are formed. 4, the viscous damping force generating section 24 generates a viscous resistance force, and the viscous damping force generating section 24 has a low rigidity spring member 14
Cooperates with and absorbs and dampens torsional vibrations. According to this embodiment, the torsional vibration of the power transmission system including the crankshaft 1 and the output shaft 23 can be reduced more effectively than in the above embodiments.
【００２２】尚、粘性減衰力発生部２４の代わりに、第
２質量体８と第３質量体４との間に、両者の相対回動時
に摩擦力を発生するフリクションワッシャ等の摩擦力発
生手段を介装するようにしてもよい。In place of the viscous damping force generating section 24, a frictional force generating means such as a friction washer for generating a frictional force between the second mass body 8 and the third mass body 4 when the two mass bodies are relatively rotated. You may make it intervene.
【００２３】[0023]
【発明の効果】以上の説明から明らかなように本発明
は、クランクシャフトに固定した第１質量体に高剛性の
ばね部材を介して第２質量体を所定角度相対回動できる
ように連繋し、この第２質量体に低剛性のばね部材を介
して第３質量体を所定角度相対回動できるように連繋す
ることにより、フライホイールへの入力トルクが小さな
場合には低剛性のばね部材のみを作用させ、第１質量体
と第２質量体をクランクシャフトとともに一体回動させ
て、クランクシャフトに第１質量体及び第２質量体の慣
性モーメントを作用させる一方、フライホイールへの入
力トルクが大きな場合には高剛性のばね部材を作用さ
せ、第１質量体をクランクシャフトとともに一体回動さ
せて、クランクシャフトに第１質量体の慣性モーメント
を作用させるようにしてあるため、クランクシャフトを
含めた動力伝達系の捩り振動をより一層効果的に低減す
ることができる。As is apparent from the above description, according to the present invention, the second mass body is connected to the first mass body fixed to the crankshaft via the highly rigid spring member so as to be relatively rotatable by a predetermined angle. By connecting the third mass body to the second mass body through the low-rigidity spring member so as to be relatively rotatable by a predetermined angle, only the low-rigidity spring member is used when the input torque to the flywheel is small. To rotate the first mass body and the second mass body together with the crankshaft to exert the moment of inertia of the first mass body and the second mass body on the crankshaft, while the input torque to the flywheel is If it is large, a high-rigidity spring member is actuated to integrally rotate the first mass body together with the crankshaft so that the moment of inertia of the first mass body acts on the crankshaft. There, it is possible to reduce the torsional vibration of the power transmission system including the crankshaft more effectively.
【図１】本発明の一実施例のフライホイールを中心軸か
ら下半分を省略して示す断面図。FIG. 1 is a sectional view showing a flywheel according to an embodiment of the present invention with a lower half omitted from a central axis.
【図２】フライホイールの作動状態図。FIG. 2 is an operation state diagram of a flywheel.
【図３】本発明の他の実施例のフライホイールを中心軸
から下半分を省略して示す断面図。FIG. 3 is a cross-sectional view showing a flywheel of another embodiment of the present invention with the lower half omitted from the central axis.
【図４】従来のフライホイールの断面図（図５のＹ−Ｙ
線に沿う断面図）。FIG. 4 is a sectional view of a conventional flywheel (Y-Y in FIG. 5).
(Cross section view along the line).
【図５】同正面図。FIG. 5 is a front view of the same.
Ａ…フライホイール、１…クランクシャフト、２…第１
質量体、４…第３質量体、８…第２質量体、１４…（低
剛性の）ばね部材、２１…（高剛性の）ばね部材。A ... flywheel, 1 ... crankshaft, 2 ... first
Mass body, 4 ... 3rd mass body, 8 ... 2nd mass body, 14 ... (low rigidity) spring member, 21 ... (high rigidity) spring member.
Claims (1)
に高剛性のばね部材を介して第２質量体を所定角度相対
回動できるように連繋し、この第２質量体に低剛性のば
ね部材を介して第３質量体を所定角度相対回動できるよ
うに連繋したことを特徴とするフライホイール。1. A low-rigidity spring member is connected to a first mass member fixed to a crankshaft via a high-rigidity spring member so that the second mass member can be relatively rotated by a predetermined angle. A flywheel characterized in that the third mass body is connected to the third mass body so as to be relatively rotatable by a predetermined angle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23452291A JPH0571588A (en) | 1991-09-13 | 1991-09-13 | Flywheel |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23452291A JPH0571588A (en) | 1991-09-13 | 1991-09-13 | Flywheel |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0571588A true JPH0571588A (en) | 1993-03-23 |
Family
ID=16972347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23452291A Pending JPH0571588A (en) | 1991-09-13 | 1991-09-13 | Flywheel |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0571588A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6964435B2 (en) | 2002-02-18 | 2005-11-15 | Walterscheid Rohrverbindungstechnik Gmbh | Coupling for connecting hydraulic ducts |
| KR101382292B1 (en) * | 2012-09-21 | 2014-04-08 | 현대자동차(주) | Apparatus for damping of flywheel |
| JP2014114946A (en) * | 2012-12-06 | 2014-06-26 | Hyundai Motor Company Co Ltd | Damping device of flywheel |
| KR101417476B1 (en) * | 2012-12-13 | 2014-07-08 | 현대자동차주식회사 | Apparatus for damping of flywheel |
| CN107345432A (en) * | 2017-07-26 | 2017-11-14 | 哈尔滨工业大学 | A kind of tuned mass damper and damping device |
| WO2018034659A1 (en) * | 2016-08-17 | 2018-02-22 | Borgwarner Inc. | Active variable stiffness absorber |
| WO2018142890A1 (en) * | 2017-02-03 | 2018-08-09 | 株式会社エクセディ | Power transmission device |
| WO2018142889A1 (en) * | 2017-02-03 | 2018-08-09 | 株式会社エクセディ | Power transmission device |
-
1991
- 1991-09-13 JP JP23452291A patent/JPH0571588A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6964435B2 (en) | 2002-02-18 | 2005-11-15 | Walterscheid Rohrverbindungstechnik Gmbh | Coupling for connecting hydraulic ducts |
| KR101382292B1 (en) * | 2012-09-21 | 2014-04-08 | 현대자동차(주) | Apparatus for damping of flywheel |
| JP2014114946A (en) * | 2012-12-06 | 2014-06-26 | Hyundai Motor Company Co Ltd | Damping device of flywheel |
| KR101417476B1 (en) * | 2012-12-13 | 2014-07-08 | 현대자동차주식회사 | Apparatus for damping of flywheel |
| WO2018034659A1 (en) * | 2016-08-17 | 2018-02-22 | Borgwarner Inc. | Active variable stiffness absorber |
| WO2018142890A1 (en) * | 2017-02-03 | 2018-08-09 | 株式会社エクセディ | Power transmission device |
| WO2018142889A1 (en) * | 2017-02-03 | 2018-08-09 | 株式会社エクセディ | Power transmission device |
| JP2018123944A (en) * | 2017-02-03 | 2018-08-09 | 株式会社エクセディ | Power transmission device |
| CN107345432A (en) * | 2017-07-26 | 2017-11-14 | 哈尔滨工业大学 | A kind of tuned mass damper and damping device |
| CN107345432B (en) * | 2017-07-26 | 2023-03-17 | 哈尔滨工业大学 | Tuned mass damper and damping device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20001114 |