JPH0674301A - Flywheel - Google Patents

Flywheel

Info

Publication number
JPH0674301A
JPH0674301A JP23012192A JP23012192A JPH0674301A JP H0674301 A JPH0674301 A JP H0674301A JP 23012192 A JP23012192 A JP 23012192A JP 23012192 A JP23012192 A JP 23012192A JP H0674301 A JPH0674301 A JP H0674301A
Authority
JP
Japan
Prior art keywords
rotating body
sub
damper mass
flywheel
crankshaft
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
Application number
JP23012192A
Other languages
Japanese (ja)
Inventor
Moriharu Hiraishi
守治 平石
Sakae Ueda
栄 植田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to JP23012192A priority Critical patent/JPH0674301A/en
Priority to DE19934328927 priority patent/DE4328927C2/en
Publication of JPH0674301A publication Critical patent/JPH0674301A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression 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
    • F16F15/131Suppression 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

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)

Abstract

PURPOSE:To improve the durability of a flywheel which reduces the torque fluctuation of a rotary system in a high temperature by making a damper mass which performs pendulous movement function as a dynamic damper. CONSTITUTION:A subrotor 10 containing a damper mass 12 which performs pendulous movement in synchronism with the rotary fluctuation which occurs in a crank shaft 1 is provided separately from a main rotor 3 which transmits drive force between clutch disks 4. The axial rigidity of the middle part 10A of the subrotor 10 is made small by thinning the middle part 10A.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【産業上の利用分野】この発明は、フライホイールの改
良に関し、特に、フライホイールが設けられる回転駆動
系の定次数のトルク変動が低減されるようにしたもので
ある。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a flywheel, and more particularly, to a constant-order torque fluctuation of a rotary drive system provided with the flywheel.

【0002】[0002]

【従来の技術】車両のエンジン等の内燃機関の駆動力
は、燃焼力をクランク機構により回転力(トルク)に変
換することにより得られるため、クランク軸等には必然
的に回転変動(トルク変動)が発生し、これが振動,騒
音の原因となる。具体的には、4サイクル4気筒エンジ
ンの場合はエンジン回転の2次成分、6気筒の場合は3
次成分の回転変動が問題となる。
2. Description of the Related Art A driving force of an internal combustion engine such as a vehicle engine is obtained by converting a combustion force into a rotational force (torque) by a crank mechanism. ) Occurs, which causes vibration and noise. Specifically, in the case of a 4-cycle 4-cylinder engine, the secondary component of engine rotation, and in the case of a 6-cylinder, it is 3
The rotational fluctuation of the next component becomes a problem.

【0003】このような問題点の解決を図る従来の技術
として、実開平1−115309号公報(第1従来例)
や、本出願人が先に提案した特願平3−274108号
明細書(第2従来例)等に記載されたものがある。即
ち、これら従来のフライホイールは、そのフライホイー
ル本体内に振り子運動可能なダンパマスを収容したもの
であって、ダンパマスの振り子運動によって内燃機関の
トルク変動を低減するようにしていた。
As a conventional technique for solving such a problem, Japanese Utility Model Laid-Open No. 1-115309 (first conventional example).
Alternatively, there are those described in the specification of Japanese Patent Application No. 3-274108 (second conventional example) previously proposed by the present applicant. That is, these conventional flywheels house a damper mass capable of pendulum motion in the flywheel body, and reduce the torque fluctuation of the internal combustion engine by the pendulum motion of the damper mass.

【0004】[0004]

【発明が解決しようとする課題】しかしながら、上記従
来の技術にあっては、トルク変動を低減するための遠心
振り子構造をフライホイール本体内に一体に設けていた
ため、トルク変動の低減とともに駆動力の伝達をも担う
フライホイール(例えば、車両のクラッチを構成するフ
ライホイール等)のように高温下にさらされる回転体に
適用した場合に、その耐久性が問題となる。
However, in the above-mentioned prior art, since the centrifugal pendulum structure for reducing the torque fluctuation is integrally provided within the flywheel body, the torque fluctuation is reduced and the driving force is reduced. When applied to a rotating body that is exposed to high temperatures, such as a flywheel that also performs transmission (for example, a flywheel that constitutes a vehicle clutch), its durability becomes a problem.

【0005】即ち、一般に高温下では材料のヤング率が
低下するため、高回転高温下においてダンパマスに作用
する遠心力を支え適正な振り子運動を行わせるために
は、ダンパマスを収容する空間を形成する壁面の肉厚等
を増して、或いは高温下における剛性の高い材料を用い
る等してフライホイールの剛性を上げる必要があるが、
壁面の肉厚等を増せばそれだけ高重量となるから慣性能
率が大きくなって応答性の低下を招くことになるし、剛
性の高い材料を用いればコストアップを招くことにもな
る。また、上記第1従来例のようにダンパマスを軸受で
支持して振り子運動をさせる構造にあっては、軸受の焼
付き防止対策も必要となる。
That is, since the Young's modulus of the material generally decreases at high temperatures, a space for accommodating the damper mass is formed in order to support the centrifugal force acting on the damper mass and to perform an appropriate pendulum motion at high rotation and high temperature. It is necessary to increase the rigidity of the flywheel by increasing the wall thickness etc. or using a material with high rigidity at high temperature,
If the wall thickness or the like is increased, the weight becomes heavier, so that the inertial performance rate increases and the responsiveness deteriorates. If a material having high rigidity is used, the cost also increases. Further, in the structure in which the damper mass is supported by the bearing to perform the pendulum motion as in the first conventional example, it is necessary to take measures to prevent seizure of the bearing.

【0006】さらに、遠心振り子構造を一体に備えたフ
ライホイールは、フライホイールの面振れによる遠心振
り子の性能低下を防ぐために、剛性の高い材料を用いる
か、或いはフライホイールの肉厚を増すなどしてフライ
ホイールの剛性を上げクランク軸の曲げ共振を常用回転
数以上に外す必要があるが、上記問題点と同様に、コス
ト及び応答性の点で問題となる。そして、クランク軸の
曲げ共振を常用回転数以上に外す方法では一つの回転次
数に対しては解決できるが、他の回転次数に対してはク
ランク軸の曲げ共振が発生するためフライホイールの面
振れによる遠心振り子の性能低下を充分に解決していな
いという未解決の課題がある。
Further, in the flywheel integrally provided with the centrifugal pendulum structure, in order to prevent the performance of the centrifugal pendulum from being deteriorated due to the surface runout of the flywheel, a highly rigid material is used or the thickness of the flywheel is increased. Therefore, it is necessary to increase the rigidity of the flywheel and eliminate the bending resonance of the crankshaft beyond the normal rotational speed. However, similar to the above problems, there are problems in cost and responsiveness. Then, the method of removing the bending resonance of the crankshaft beyond the normal rotation speed can solve one rotation order, but the bending resonance of the crankshaft occurs for other rotation orders, so the surface deflection of the flywheel occurs. There is an unsolved problem that the deterioration of the performance of the centrifugal pendulum due to the above is not sufficiently solved.

【0007】本発明は、このような従来の技術が有する
未解決の課題に着目してなされたものであって、特に、
遠心振り子構造によりトルク変動を低減するフライホイ
ールの高温下における耐久性の向上を図ることを目的と
している。
The present invention has been made by paying attention to the unsolved problems of the conventional techniques as described above.
The centrifugal pendulum structure aims to improve the durability of the flywheel at high temperatures, which reduces torque fluctuations.

【0008】[0008]

【課題を解決するための手段】上記目的を達成するため
に、請求項1記載の発明は、振り子運動をするダンパマ
スを収容したトルク変動低減用の副回転体を、駆動力伝
達用の主回転体とは別個に設けた。また、請求項2記載
の発明は、上記請求項1記載の発明において、副回転体
のダンパマス収容位置の径方向内側の部分の軸方向の剛
性を小さくした。
In order to achieve the above object, the invention according to claim 1 uses a sub-rotor for reducing torque fluctuations, which accommodates a damper mass that makes a pendulum motion, and a main rotation for transmitting driving force. It was provided separately from the body. In the invention according to claim 2, in the invention according to claim 1, the rigidity in the axial direction of the portion of the sub-rotor radially inside the damper mass housing position is reduced.

【0009】そして、請求項3記載の発明は、上記請求
項1又は請求項2記載の発明において、副回転体を、そ
の径方向内側の縁部分を介して主回転体に結合した。さ
らに、請求項4記載の発明は、上記請求項1乃至請求項
3記載の発明において、ダンパマスを、主回転体の外径
より径方向外側に位置させた。
According to a third aspect of the present invention, in the above-mentioned first or second aspect of the present invention, the sub-rotating body is coupled to the main rotating body via the radially inner edge portion. Further, in the invention according to claim 4, in the invention according to any one of claims 1 to 3, the damper mass is located radially outside of the outer diameter of the main rotating body.

【0010】[0010]

【作用】請求項1記載の発明にあっては、クラッチにお
ける摩擦熱等により高温下にさらされる駆動力伝達用の
主回転体と、トルク変動低減用の副回転体とが別体であ
るため、主回転体の熱が直接ダンパマスやこれを収容す
る空間を形成する壁面等に作用することがなく、従っ
て、熱対策のために副回転体のダンパマス収容空間を形
成する壁面の肉厚等を増す必要がない。
According to the first aspect of the invention, the main rotating body for transmitting the driving force and the auxiliary rotating body for reducing the torque fluctuation, which are exposed to a high temperature due to frictional heat in the clutch, are separate bodies. , The heat of the main rotating body does not directly act on the damper mass or the wall surface forming the space for accommodating the same, and therefore the wall thickness of the wall surface forming the damper mass accommodating space of the sub rotating body should be adjusted to prevent heat. No need to increase.

【0011】そして、回転駆動系のトルク変動は、主に
副回転体に収容されたダンパマスの振り子運動によって
低減されるため、主回転体は主に駆動力の伝達を担えば
よくなるから、かかる主回転体の質量をトルク変動低減
のために大きくする必要もほとんどない。このようなこ
とから、駆動力伝達用の主回転体内にダンパマスを収容
する構造に比べて、フライホイール全体としての軽量化
が図られるため、応答性も向上する。
Since the torque fluctuation of the rotary drive system is reduced mainly by the pendulum motion of the damper mass housed in the sub rotary body, the main rotary body needs only to mainly transfer the driving force. There is almost no need to increase the mass of the rotating body to reduce the torque fluctuation. For this reason, the flywheel as a whole can be made lighter than the structure in which the damper mass is housed in the main rotating body for transmitting the driving force, and the responsiveness is also improved.

【0012】また、請求項2記載の発明のように、副回
転体の径方向内側の部分の軸方向剛性が小さい構造であ
ると、かかる副回転体はいわゆるフレキシブルフライホ
イールとして機能するため、この副回転体が取り付けら
れる回転軸の曲げ共振を容易に常用回転数以下に外すこ
とができ、ダンパマスのスムーズな振り子運動が確保さ
れる。
Further, in the structure according to the second aspect of the present invention, when the radial inner portion of the sub-rotor has a small axial rigidity, the sub-rotor functions as a so-called flexible flywheel. The bending resonance of the rotary shaft to which the sub-rotor is attached can be easily removed below the normal rotational speed, and a smooth pendulum motion of the damper mass is secured.

【0013】そして、請求項3記載の発明であれば、副
回転体を主回転体に結合しているため、副回転体自身は
主回転体とは別個のものであっても、取付け時の作業性
等を特に悪くすることがなく、しかも副回転体は径方向
内側の縁部分を介して主回転体に結合されるので、それ
ら回転体間の接触面積が小さく熱の伝達率は低い。さら
に、請求項4記載の発明であれば、副回転体に収容され
ているダンパマスが、主回転体からの輻射熱を受け難い
位置にあるため、主回転体に発生した熱のダンパマスへ
の影響がより小さくなる。
According to the third aspect of the present invention, since the sub-rotating body is connected to the main rotating body, even if the sub-rotating body itself is separate from the main rotating body, the sub-rotating body can be easily mounted. The workability and the like are not particularly deteriorated, and since the sub-rotating body is coupled to the main rotating body via the edge portion on the radially inner side, the contact area between the rotating bodies is small and the heat transfer coefficient is low. Further, according to the invention of claim 4, since the damper mass housed in the sub-rotor is in a position where it is difficult to receive the radiant heat from the main rotor, the influence of the heat generated in the main rotor on the damper mass is exerted. It gets smaller.

【0014】[0014]

【実施例】以下、この発明の実施例を図面に基づいて説
明する。図1及び図2は本発明の第1実施例を示す図で
あり、この実施例は、本発明に係るフライホイールを車
両の駆動力伝達部に適用したものである。先ず、構成を
説明すると、図1に示すように、車両用エンジンのクラ
ンク軸1及びマニュアル・トランスミッションの入力軸
2は同軸上に配設されていて、それらクランク軸1と入
力軸2との間では、クランク軸1の端部に同軸に固定さ
れた主回転体3と、入力軸2の端部に同軸に固定された
クラッチディスク4との間の摩擦力を介して断続的に駆
動力伝達可能となっている。なお、主回転体3及びクラ
ッチディスク4間の断続機構は従来の車両用クラッチと
同様である。
Embodiments of the present invention will be described below with reference to the drawings. 1 and 2 are views showing a first embodiment of the present invention, in which the flywheel according to the present invention is applied to a driving force transmitting portion of a vehicle. First, the structure will be described. As shown in FIG. 1, a crankshaft 1 of a vehicle engine and an input shaft 2 of a manual transmission are coaxially arranged, and the crankshaft 1 and the input shaft 2 are arranged between the crankshaft 1 and the input shaft 2. Then, the driving force is intermittently transmitted through the frictional force between the main rotor 3 coaxially fixed to the end of the crankshaft 1 and the clutch disc 4 coaxially fixed to the end of the input shaft 2. It is possible. The connecting / disconnecting mechanism between the main rotating body 3 and the clutch disc 4 is similar to that of the conventional vehicle clutch.

【0015】主回転体3は、中央部3A及び周縁部3B
間を中央部3A側が小径となるテーパ部3Cとすること
により、中央部3Aが周縁部3Bよりも車両用エンジン
側に凹んだ円板状に形成されている。なお、主回転体3
の周縁部3Bのクラッチディスク4側を向く面には、ク
ラッチディスク4を覆うようにクラッチカバー5が固定
されている。
The main rotating body 3 has a central portion 3A and a peripheral portion 3B.
By making the space a tapered portion 3C having a smaller diameter on the central portion 3A side, the central portion 3A is formed in a disc shape recessed toward the vehicle engine side than the peripheral edge portion 3B. The main rotating body 3
A clutch cover 5 is fixed to the surface of the peripheral edge portion 3B facing the clutch disc 4 side so as to cover the clutch disc 4.

【0016】また、クランク軸1の主回転体3固定位置
の図1左方(エンジン側)には、トルク変動低減用の副
回転体10がクランク軸1と同軸に固定されていて、こ
れら主回転体3及び副回転体10によってフライホイー
ル20が構成される。そして、副回転体10は、比較的
薄く形成することにより軸方向の剛性が小さくなってい
る中央部10Aと、複数の転動室11を形成する周縁部
10Bと、この転動室11の開口側を封止するカバー1
0Cとから構成されていて、カバー10Cを取り外した
状態の副回転体10の平面図である図2に示すように、
周縁部10Bには、周方向に等間隔に同形状の複数(本
実施例では12個)の転動室11,…,11が形成され
ている。
Further, on the left side (engine side) in FIG. 1 of the fixed position of the main shaft 3 of the crankshaft 1, a sub rotary member 10 for reducing torque fluctuation is fixed coaxially with the crankshaft 1. The rotary body 3 and the sub-rotary body 10 constitute a flywheel 20. The sub-rotational body 10 has a central portion 10A, which has a relatively small axial rigidity due to being formed relatively thin, a peripheral portion 10B which forms a plurality of rolling chambers 11, and an opening of the rolling chamber 11. Cover 1 that seals the side
0C, as shown in FIG. 2 which is a plan view of the sub-rotating body 10 with the cover 10C removed.
A plurality of (12 in this embodiment) rolling chambers 11, ..., 11 having the same shape are formed in the peripheral portion 10B at equal intervals in the circumferential direction.

【0017】各転動室11は副回転体10に対して略並
行に凹んだ円弧状の凹部からなり、各転動室11内に
は、かかる副回転体10が回転する際の遠心力によりそ
の転動室11の径方向外側の内側面を転動しつつ振り子
運動をする厚めの円板からなるダンパマス12が収容さ
れている。なお、転動室11の径方向及び厚さ方向の寸
法は、ダンパマス12の転動が可能な範囲で最も小さく
することが望ましい。
Each rolling chamber 11 is composed of an arcuate recess which is recessed substantially parallel to the sub-rotating body 10. Inside each rolling chamber 11, centrifugal force is generated when the sub-rotating body 10 rotates. A damper mass 12 made of a thick disk that accommodates a pendulum motion while rolling on the radially inner surface of the rolling chamber 11 is accommodated. The dimensions of the rolling chamber 11 in the radial direction and the thickness direction are preferably the smallest in the range in which the damper mass 12 can roll.

【0018】そして、各転動室11の内側面は、ダンパ
マス12の振り子運動の軌跡が遠心振り子の理論を満足
するように形成する。具体的には、ダンパマス12の質
量をmd 、ダンパマス12の慣性能率をId、ダンパマ
ス12の半径をrd 、クランク軸1のトルク変動次数を
nとした場合に、副回転体10の回転中心からダンパマ
ス12の振り子運動の支点までの距離Rと、ダンパマス
12の振り子運動の支点からそのダンパマス12の重心
までの距離Lとの比率R/Lを、 R/L=n2 {1+Id /(md ・rd 2 )} という関係に設定する。なお、本実施例では、複数のダ
ンパマス12を有しているため、質量md 及び慣性能率
d はいずれもそれら複数のダンパマス12のトータル
の値である。
The inner surface of each rolling chamber 11 is formed so that the trajectory of the pendulum motion of the damper mass 12 satisfies the theory of the centrifugal pendulum. Specifically, when the mass of the damper mass 12 is m d , the inertia ratio of the damper mass 12 is I d , the radius of the damper mass 12 is r d , and the torque fluctuation order of the crankshaft 1 is n, the rotation of the sub-rotating body 10 the distance R to the fulcrum of the pendulum motion of the damper mass 12 from the center, the ratio R / L of the distance L from the fulcrum of the pendulum motion of the damper mass 12 to the center of gravity of the damper mass 12, R / L = n 2 {1 + I d / (M d · r d 2 )} is set. Since the present embodiment has a plurality of damper masses 12, both the mass m d and the inertial performance rate I d are total values of the plurality of damper masses 12.

【0019】そして、主回転体3及び副回転体10は、
それらの中心部分に開けられた孔部3a,10aをクラ
ンク軸1の端面に形成された凸部1Aに嵌め込むととも
に、中央部3Aのクラッチディスク4側を向く面からボ
ルト孔3b,10bを通じてクランク軸1の大径部1B
にボルト6を締結することにより、回転方向及び軸方向
に一体となるようにクランク軸1に固定されている。な
お、中央部3A,10Aのボルト孔3b,10bの径方
向外側の位置には、主回転体3及び副回転体10間の相
対的な位置決めをするロケートピン7が嵌め込まれてい
る。
The main rotary body 3 and the sub rotary body 10 are
The holes 3a and 10a formed in the central portions of the crankshaft 1 are fitted into the convex portions 1A formed on the end surface of the crankshaft 1, and the crankshaft is cranked through the bolt holes 3b and 10b from the surface of the central portion 3A facing the clutch disc 4 side. Large diameter part 1B of shaft 1
The bolt 6 is fastened to the crankshaft 1 so as to be integrated in the rotational direction and the axial direction. A locating pin 7 for relative positioning between the main rotating body 3 and the sub-rotating body 10 is fitted at a position radially outside the bolt holes 3b, 10b of the central portions 3A, 10A.

【0020】また、副回転体10の周縁部10Bは、そ
の中央部10Aの径方向寸法と、主回転体3のテーパ部
3Cの傾斜角等を適宜選定することにより、副回転体1
0が軸方向にたわんだ際であっても主回転体3に接触し
ない程度の位置に配置してある。次に、本実施例の作用
効果を説明する。
In the peripheral portion 10B of the sub-rotating body 10, the sub-rotating body 1 is appropriately selected by appropriately selecting the radial dimension of the central portion 10A and the inclination angle of the taper portion 3C of the main rotating body 3.
It is arranged at a position where it does not come into contact with the main rotating body 3 even when 0 is bent in the axial direction. Next, the function and effect of this embodiment will be described.

【0021】エンジンで発生した駆動力は、クランク軸
1,主回転体3,クラッチディスク4及び入力軸2を介
してマニュアル・トランスミッションに入力される。そ
して、クランク軸1には、4気筒エンジンであれば主と
して2次のトルク変動が生じ、6気筒エンジンであれば
主として3次のトルク変動が生じることになるが、かか
るトルク変動は、ダンパマス12の振り子運動により吸
収し低減することができる。
The driving force generated by the engine is input to the manual transmission via the crankshaft 1, the main rotor 3, the clutch disc 4 and the input shaft 2. Then, in the crankshaft 1, if the engine is a 4-cylinder engine, a secondary torque fluctuation mainly occurs, and if it is a 6-cylinder engine, a tertiary torque fluctuation mainly occurs. It can be absorbed and reduced by the pendulum movement.

【0022】即ち、クランク軸1にトルク変動が伝達さ
れ、副回転体10にもそのトルク変動が伝達されると、
距離R及びLの比率を上述したように遠心振り子の理論
を満足するように選定している結果、転動室11内に収
容されたダンパマス12がトルク変動に同期した振り子
運動をし、これがダイナミックダンパとして作用するよ
うになるから、副回転体10に伝達されたトルク変動が
ダンパマス12の重心位置の変動によって確実に低減さ
れるようになり、これが取り付けられたクランク軸1の
トルク変動が大幅に低減し、車室内の騒音低減が図られ
るのである。
That is, when the torque fluctuation is transmitted to the crankshaft 1 and the torque fluctuation is transmitted to the sub-rotor 10,
As a result of selecting the ratio of the distances R and L so as to satisfy the theory of the centrifugal pendulum as described above, the damper mass 12 housed in the rolling chamber 11 makes a pendulum motion in synchronization with the torque fluctuation, which is a dynamic phenomenon. Since it acts as a damper, the torque fluctuation transmitted to the sub-rotational body 10 is surely reduced by the fluctuation of the center of gravity of the damper mass 12, and the torque fluctuation of the crankshaft 1 to which this is attached is significantly reduced. Therefore, the noise in the passenger compartment can be reduced.

【0023】また、副回転体10の中央部10Aを比較
的薄く形成している結果、この部分の軸方向の剛性が小
さくなっているので、クランク軸1及び副回転体10で
形成される系の曲げ共振を容易に常用回転数以下に外す
ことができ、曲げ共振によるこもり音の低減が図られる
とともに、クランク軸1自身も従来の曲げ剛性を確保す
る必要がなくなり、クランク軸1自身の軽量化が図られ
る。しかも、副回転体10はいわゆるフレキシブルフラ
イホイールとして機能する結果、副回転体10の周縁部
10Bの面振れが防止され、ダンパマス12のスムーズ
な転動が確保されるという利点もある。なお、クランク
軸1及び主回転体3で形成される系の曲げ共振は、駆動
力の伝達を担う主回転体3の剛性を下げることはできな
いので、逆に剛性を高めることにより常用回転数以上に
外す必要がある。
Further, since the central portion 10A of the sub-rotating body 10 is formed relatively thin, the rigidity of this portion in the axial direction is reduced, so that the system formed by the crankshaft 1 and the sub-rotating body 10 is formed. The bending resonance of can be easily removed below the normal rotational speed, the muffled noise due to the bending resonance can be reduced, and the crankshaft 1 itself does not need to secure the conventional bending rigidity, and the crankshaft 1 itself is lightweight. Be promoted. Moreover, as a result of the sub-rotating body 10 functioning as a so-called flexible flywheel, there is an advantage that the surface runout of the peripheral edge portion 10B of the sub-rotating body 10 is prevented and the smooth rolling of the damper mass 12 is secured. Bending resonance of the system formed by the crankshaft 1 and the main rotating body 3 cannot reduce the rigidity of the main rotating body 3 that transmits the driving force. Need to be removed.

【0024】そして、クランク軸1及び入力軸2間の駆
動力の伝達は、従来の車両と同様に主回転体3及びクラ
ッチディスク4間の摩擦力を介して行われるのである
が、クランク軸1のトルク変動は上述したように副回転
体10において低減されるため、主回転体3は主として
駆動力の伝達を担えばよいことになり、従って、主回転
体3の質量をトルク変動を吸収するために大きくする必
要がなく、クラッチディスク4との摩擦によって温度が
上昇した際の熱容量の点からその厚み等を選定すればよ
い。
The transmission of the driving force between the crankshaft 1 and the input shaft 2 is performed via the frictional force between the main rotating body 3 and the clutch disc 4 as in the conventional vehicle. As described above, since the torque fluctuation of 1 is reduced in the sub-rotating body 10, the main rotating body 3 has only to mainly transfer the driving force, and therefore the mass of the main rotating body 3 absorbs the torque fluctuation. Therefore, it is not necessary to increase the thickness, and the thickness or the like may be selected from the viewpoint of the heat capacity when the temperature rises due to friction with the clutch disc 4.

【0025】さらに、転動室11が形成された副回転体
10の周縁部10Bは、クラッチディスク4との摩擦に
より高温になる主回転体3とは非接触であるため、転動
室11の壁面の厚みを特に厚くする等の熱対策が不要と
なり、しかも副回転体10の中央部10Aは薄く形成さ
れているため、この副回転体10を別個に設けたことに
よる重量の増加分はそれほど多くはない。
Further, since the peripheral portion 10B of the sub-rotating body 10 in which the rolling chamber 11 is formed is not in contact with the main rotating body 3 which is heated to a high temperature by friction with the clutch disc 4, the rolling chamber 11 is Since heat countermeasures such as making the wall thickness particularly thick are unnecessary, and since the central portion 10A of the sub-rotating body 10 is formed thin, the weight increase due to providing the sub-rotating body 10 separately is not so great. Not many.

【0026】むしろ、遠心振り子構造を有する副回転体
10を別個に設けている分、上述したようにクランク軸
1や主回転体3等の軽量化が図られるから、遠心振り子
構造を主回転体3内に一体に設ける従来のフライホイー
ルの構造と比較して回転系全体としては軽量になり、応
答性の向上を図ることができる。また、転動室11の径
方向及び厚さ方向の寸法を、ダンパマス12の転動が可
能な範囲で最も小さくすると、始動時において発生する
異音をも低減できるという利点がある。
Rather, since the auxiliary rotary body 10 having the centrifugal pendulum structure is separately provided, the weight of the crankshaft 1, the main rotary body 3, etc. can be reduced as described above. Therefore, the centrifugal pendulum structure is used as the main rotary body. As compared with the structure of a conventional flywheel provided integrally in the inside of 3, the rotation system as a whole becomes lighter in weight, and the responsiveness can be improved. Further, when the dimensions of the rolling chamber 11 in the radial direction and the thickness direction are made as small as possible within the range in which the damper mass 12 can roll, there is an advantage that abnormal noise generated at the time of starting can be reduced.

【0027】図3及び図4は本発明の第2実施例を示す
図であり、本実施例も上記第1実施例と同様に、本発明
に係るフライホイールを車両の駆動力伝達部に適用した
ものである。なお、上記第1実施例の構成と同等の部材
及び部位には、同じ符号を付し、その重複する説明は省
略する。即ち、本実施例では、副回転体10を主回転体
3とは別個に設けるという点は上記第1実施例と同様で
あるが、その副回転体10を直接クランク軸1に固定す
るのではなく、副回転体10を径方向縁側の縁部分を介
して主回転体3に固定するとともに、副回転体10とク
ランク軸1との間を非接触としたものである。
FIGS. 3 and 4 are views showing a second embodiment of the present invention. In this embodiment as well, as in the first embodiment, the flywheel according to the present invention is applied to a driving force transmitting portion of a vehicle. It was done. The same members and parts as those in the configuration of the first embodiment are designated by the same reference numerals, and the duplicated description will be omitted. That is, this embodiment is similar to the first embodiment in that the auxiliary rotary body 10 is provided separately from the main rotary body 3, but the auxiliary rotary body 10 is not fixed directly to the crankshaft 1. Instead, the auxiliary rotary body 10 is fixed to the main rotary body 3 via the edge portion on the radial edge side, and the auxiliary rotary body 10 and the crankshaft 1 are not in contact with each other.

【0028】具体的には、フライホイール20を図3左
方から見た平面図である図4にも示すように、副回転体
10の孔部10aの内径をクランク軸1の大径部1Bの
外径よりも大きくするとともに、その孔部10aの周方
向4箇所に凸部10cを設けここにボルト孔10dを形
成し、そしてボルト孔10dを通じてボルト13を主回
転体3の中央部3Aに締結することにより、副回転体1
0が主回転体3に結合されている。
More specifically, as shown in FIG. 4, which is a plan view of the flywheel 20 as viewed from the left in FIG. 3, the inner diameter of the hole 10a of the sub-rotor 10 is set to the large diameter portion 1B of the crankshaft 1. And a bolt hole 10d is formed at four convex portions 10c in the circumferential direction of the hole portion 10a, and the bolt 13 is attached to the central portion 3A of the main rotating body 3 through the bolt hole 10d. By fastening, the sub-rotor 1
0 is connected to the main rotating body 3.

【0029】このような構成であると、副回転体10は
主回転体3にのみ接触し、且つ、それら主回転体3及び
副回転体10間の接触面積も上記第1実施例に比べて極
めて小さくなる(図4の破線で示す領域だけになる)の
で、主回転体3で発生した摩擦熱のほとんどがクランク
軸1側に流れるようになり、副回転体10の温度上昇を
さらに低減することができる。
With this structure, the sub-rotating body 10 contacts only the main rotating body 3, and the contact area between the main rotating body 3 and the sub-rotating body 10 is also different from that of the first embodiment. Since it becomes extremely small (only in the region shown by the broken line in FIG. 4), most of the friction heat generated in the main rotor 3 flows to the crankshaft 1 side, and the temperature rise of the auxiliary rotor 10 is further reduced. be able to.

【0030】そして、副回転体10が主回転体3に結合
されていれば、組立時の作業性も向上するという利点が
あり、さらには、主回転体3の中央部3Aの厚みを増す
ことが容易となるから、主回転体3の剛性を上げる上で
も有利である。その他の作用効果は上記第1実施例と同
様である。図5は本発明の第3実施例を示す図である。
If the sub-rotating body 10 is connected to the main rotating body 3, there is an advantage that workability at the time of assembling is improved, and further, the thickness of the central portion 3A of the main rotating body 3 is increased. Since it becomes easier, it is also advantageous in increasing the rigidity of the main rotating body 3. Other functions and effects are similar to those of the first embodiment. FIG. 5 is a diagram showing a third embodiment of the present invention.

【0031】即ち、本実施例では、基本的な構成は上記
第2実施例と同様であるが、副回転体10のダンパマス
を収容する周縁部10Bを、主回転体3の外径より径方
向外側に位置するようにしている。このような構成であ
ると、主回転体3からの輻射熱を受け難い位置にダンパ
マスが位置することになるから、熱対策の点でさらに有
利になるし、ダンパマスが副回転体10の回転中心から
より遠い位置にある分、発生する遠心力が大きくなりト
ルク変動の低減効果が大きくなるという利点もある。
That is, in this embodiment, the basic structure is the same as that of the second embodiment, but the peripheral portion 10B for accommodating the damper mass of the sub-rotating body 10 is arranged in the radial direction from the outer diameter of the main rotating body 3. It is located outside. With such a configuration, the damper mass is located at a position where it is difficult to receive the radiant heat from the main rotating body 3, which is more advantageous in terms of heat countermeasures, and the damper mass is located closer to the rotation center of the sub rotating body 10. The further the position is, the greater the centrifugal force that occurs and the greater the effect of reducing torque fluctuations.

【0032】さらには、副回転体10の中央部10Aの
径方向寸法も大きくなるため、この部分の板厚をそれほ
ど薄く加工しなくても実質的な曲げ剛性が下がる結果、
フレキシブルフライホイールとしての機能を発揮し易く
なるという利点もある。つまり、中央部10Aは周縁部
10Bよりも主回転体3からの熱伝導の影響を受け易い
ため、高温下における剛性を上げるために板厚は厚いほ
うが望ましい反面、ここを厚くするとフレキシブルフラ
イホイールとして機能し難くなるという不具合があるの
であるが、本実施例の構成であれば、高温下における剛
性を上げるという要求と、フレキシブルフライホイール
として機能させるという要求との両方を満足させること
ができるのである。
Furthermore, since the radial dimension of the central portion 10A of the sub-rotating body 10 also becomes large, the bending rigidity is substantially reduced without processing the plate thickness of this portion so much.
There is also an advantage that the function as a flexible flywheel can be easily exhibited. In other words, the central portion 10A is more easily affected by heat conduction from the main rotating body 3 than the peripheral portion 10B. Therefore, it is desirable that the plate thickness be thick in order to increase the rigidity at high temperatures. Although there is a problem that it becomes difficult to function, the configuration of this embodiment can satisfy both the requirement of increasing the rigidity at high temperature and the requirement of functioning as a flexible flywheel. .

【0033】その他の作用効果は上記第1実施例と同様
である。なお、上記各実施例では、本発明に係るフライ
ホイールをマニュアル・トランスミッションを有する車
両の駆動力伝達系に適用した場合について説明したが、
本発明の適用対象はこれに限定されるものではない。例
えば、オートマチック・トランスミッションを有する車
両であっても、そのオートマチック・トランスミッショ
ンに含まれるトルク・コンバータを構成する駆動力伝達
用のポンプとは別個に上記各実施例で説明した副回転体
10を設ければ、上記実施例と同等の作用効果を得るこ
とができる。さらには、車両の駆動力伝達系以外の回転
系であっても本発明は適用可能である。
Other functions and effects are similar to those of the first embodiment. In each of the above embodiments, the case where the flywheel according to the present invention is applied to the driving force transmission system of a vehicle having a manual transmission has been described.
The application target of the present invention is not limited to this. For example, even in a vehicle having an automatic transmission, the sub-rotating body 10 described in each of the above embodiments is provided separately from the pump for transmitting driving force which constitutes the torque converter included in the automatic transmission. In this case, it is possible to obtain the same effect as that of the above embodiment. Furthermore, the present invention can be applied to a rotating system other than the driving force transmission system of the vehicle.

【0034】[0034]

【発明の効果】以上説明したように、本発明によれば、
振り子運動をするダンパマスを収容したトルク変動低減
用の副回転体を、駆動力伝達用の主回転体とは別個に設
ける構成としたため、高温下における耐久性が向上する
という効果がある。特に、請求項2記載の発明であれ
ば、副回転体はフレキシブルフライホイールとして機能
するため、曲げ共振を容易に常用回転数以下に外すこと
ができるから、こもり音の低減等も図れるし、副回転体
の面振れが防止される結果、ダンパマスのスムーズな振
り子運動が確保されるという効果がある。
As described above, according to the present invention,
Since the sub-rotary body for reducing the torque fluctuation, which accommodates the damper mass that makes the pendulum motion, is provided separately from the main rotary body for transmitting the driving force, the durability at high temperature is improved. In particular, according to the second aspect of the present invention, since the sub-rotor functions as a flexible flywheel, bending resonance can be easily removed below the normal rotational speed, so that muffled sound can be reduced and the like. As a result of the surface wobbling of the rotating body being prevented, a smooth pendulum motion of the damper mass is secured.

【0035】また、請求項3記載の発明であれば、組立
時の作業性の向上が図られるとともに、副回転体の熱対
策がより有利になる。さらに、請求項4記載の発明であ
れば、主回転体からの輻射熱を受け難い位置にダンパマ
スが位置することになるから、熱対策の点でさらに有利
になるし、ダンパマスが副回転体の回転中心からより遠
い位置にある分、発生する遠心力が多くなり、トルク変
動の低減効果が大きくなり、しかも、フレキシブルフラ
イホイールとしての機能を発揮し易くなるという効果が
ある。
According to the third aspect of the invention, the workability at the time of assembly can be improved, and the measure against heat of the sub-rotating body becomes more advantageous. Further, according to the invention of claim 4, since the damper mass is located at a position where it is hard to receive the radiant heat from the main rotating body, it is more advantageous in terms of heat countermeasures, and the damper mass can rotate the sub rotating body. The more distant from the center, the more centrifugal force is generated, the greater the effect of reducing torque fluctuations, and the more easily the function as a flexible flywheel is exerted.

【図面の簡単な説明】[Brief description of drawings]

【図1】第1実施例の構成を示す側断面図である。FIG. 1 is a side sectional view showing a configuration of a first embodiment.

【図2】副回転体の平面図である。FIG. 2 is a plan view of a sub rotary body.

【図3】第2実施例の構成を示す側断面図である。FIG. 3 is a side sectional view showing a configuration of a second embodiment.

【図4】フライホイールの平面図である。FIG. 4 is a plan view of a flywheel.

【図5】第3実施例の構成を示す概略図である。FIG. 5 is a schematic diagram showing a configuration of a third exemplary embodiment.

【符号の説明】[Explanation of symbols]

1 クランク軸 2 入力軸 3 主回転体 3A 中央部 3B 周縁部 3C テーパ部 4 クラッチディスク 10 副回転体 10A 中央部 10B 周縁部 10C カバー 11 転動室 12 ダンパマス 20 フライホイール 1 Crankshaft 2 Input Shaft 3 Main Rotating Body 3A Central Part 3B Peripheral Part 3C Tapered Part 4 Clutch Disc 10 Sub-Rotating Body 10A Central Part 10B Peripheral Part 10C Cover 11 Rolling Chamber 12 Damper Mass 20 Flywheel

Claims (4)

【特許請求の範囲】[Claims] 【請求項1】 振り子運動をするダンパマスを収容した
トルク変動低減用の副回転体を、駆動力伝達用の主回転
体とは別個に設けたことを特徴とするフライホイール。
1. A flywheel comprising: a torque-reducing sub-rotor for accommodating a pendulum-moving damper mass, the sub-rotator being provided separately from a drive-power-transmitting main rotor.
【請求項2】 副回転体のダンパマス収容位置の径方向
内側の部分の軸方向の剛性を小さくした請求項1記載の
フライホイール。
2. The flywheel according to claim 1, wherein a radial inner side portion of the sub rotor having a damper mass accommodating position has reduced axial rigidity.
【請求項3】 副回転体を、その径方向内側の縁部分を
介して主回転体に結合した請求項1又は請求項2記載の
フライホイール。
3. The flywheel according to claim 1, wherein the sub-rotating body is connected to the main rotating body via an edge portion on the radially inner side of the sub-rotating body.
【請求項4】 ダンパマスを、主回転体の外径より径方
向外側に位置させた請求項1乃至請求項3のいずれかに
記載のフライホイール。
4. The flywheel according to claim 1, wherein the damper mass is located radially outside of the outer diameter of the main rotating body.
JP23012192A 1992-08-28 1992-08-28 Flywheel Pending JPH0674301A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP23012192A JPH0674301A (en) 1992-08-28 1992-08-28 Flywheel
DE19934328927 DE4328927C2 (en) 1992-08-28 1993-08-27 flywheel

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP23012192A JPH0674301A (en) 1992-08-28 1992-08-28 Flywheel

Publications (1)

Publication Number Publication Date
JPH0674301A true JPH0674301A (en) 1994-03-15

Family

ID=16902900

Family Applications (1)

Application Number Title Priority Date Filing Date
JP23012192A Pending JPH0674301A (en) 1992-08-28 1992-08-28 Flywheel

Country Status (2)

Country Link
JP (1) JPH0674301A (en)
DE (1) DE4328927C2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
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WO2004051115A1 (en) * 2002-12-04 2004-06-17 Aichi Kikai Kogyo Kabushiki Kaisya Flywheel
CN103410915A (en) * 2013-09-10 2013-11-27 重庆大学 Multi-level dual mass flywheel with inertia balancing mechanism

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2606292Y2 (en) * 1993-08-18 2000-10-10 ヴァレオユニシアトランスミッション株式会社 Flywheel
DE19913015B4 (en) 1999-03-23 2009-06-04 Zf Sachs Ag Vibration damping system
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US7219578B2 (en) 2002-12-04 2007-05-22 Aichi Kikai Kogyo Kabushiki Kaisha Flywheel
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CN103410915A (en) * 2013-09-10 2013-11-27 重庆大学 Multi-level dual mass flywheel with inertia balancing mechanism
CN103410915B (en) * 2013-09-10 2015-04-01 重庆大学 Multi-level dual mass flywheel with inertia balancing mechanism

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DE4328927C2 (en) 2000-05-18

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