JPH02502303A - Torsional vibration isolation device and method - Google Patents
Torsional vibration isolation device and methodInfo
- Publication number
- JPH02502303A JPH02502303A JP61504795A JP50479586A JPH02502303A JP H02502303 A JPH02502303 A JP H02502303A JP 61504795 A JP61504795 A JP 61504795A JP 50479586 A JP50479586 A JP 50479586A JP H02502303 A JPH02502303 A JP H02502303A
- Authority
- JP
- Japan
- Prior art keywords
- crankshaft
- flywheel
- internal combustion
- rotating
- 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.)
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Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/78—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16F15/14—Suppression 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
- F16F15/1407—Suppression 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
- F16F15/1414—Masses driven by elastic elements
- F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
- F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるため要約のデータは記録されません。 (57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】 ねじり振動分離装置および方法 発明の分野および背景 本発明は多シリンダ内燃機関に関し、特にクランク軸およびフライホイールで形 成された回転装置をねじり振動が誘起する応力から防護する装置を有する多シリ ンダ内燃機関に関する。[Detailed description of the invention] Torsional vibration isolation device and method Field and background of the invention The present invention relates to multi-cylinder internal combustion engines, and in particular to crankshafts and flywheels. A multi-series system with a device to protect rotary equipment from stresses induced by torsional vibrations. regarding internal combustion engines.
多シリンダ内燃機関のクランク軸とフライホイールとが構成要素の慣性モーメン トおよび継手のせいで、ねじり振動の自然振動数または共鳴振動数を有する回転 系を形成することが認められて久しくなる。エンジンのシリンダが着火する結果 、クランク軸に加わる脈動力がそうしたねじり振動を誘起し、ある回転速度にお いては、クランク軸また力を生む。Moment of inertia of the crankshaft and flywheel of a multi-cylinder internal combustion engine rotation with a natural or resonant frequency of torsional vibration due to the It has been a long time since it was recognized that they form a system. Result of engine cylinder ignition , the pulsating force applied to the crankshaft induces such torsional vibration, and at a certain rotational speed. The crankshaft also generates force.
本発明の分野における重要な参考文献(1979年8月6〜9日オレゴン州ポー トランドにおける西海岸国際会議におけるRObsrt O,Bremer、 Jr、提出のB、1.1!、、論文sp −445)に示されて偽るごとく、本 発明の分野においてねじり振動および応力を取扱う際の通常のアプローチはクラ ンク軸/7ライホイール系が一つの簡単なねじり振動子であるかのごとく分析す ることである。このような分析へのアプローチにおいて、構成要素の慣性モーメ ントはフライホイールに最も近いクランクビンの周りで再分解され、系はピンが あたかもビンより前方のクランク軸の部分を7ライホイールと連結するばねであ るかのごとく扱われる。その場合、この系はそのねじり振動の自然振動数を決定 するねじりばね率を有する弾性コネクタ(ビン)によって連結された二つの質量 (クランク軸およびフライホイール)として見ることができる。その場合、この 系はエンジンの作動範囲(毎分当りの回転数において)に入る調和振動数、また は応力を発生し恐らく破壊的になるような方法において他の振動数と結合するv I4和振動数を求めて分析される。このような振動数が発見されるので、ダンパ はエネルギを消散させることによって振動を減衰または減少させるためフライホ イールから遠い方のクランク軸端に取付けられるように設計されている。Important References in the Field of the Invention (Port, Oregon, August 6-9, 1979) RObsrt O, Bremer, at the West Coast International Conference in Tolland Jr. Submission B, 1.1! ,, as falsely shown in the paper sp-445), the book The usual approach when dealing with torsional vibrations and stresses in the field of invention is to Analyze the link shaft/7raiwheel system as if it were a simple torsional oscillator. Is Rukoto. In this approach to analysis, the moment of inertia of the component is The pins are redisassembled around the crankbin closest to the flywheel, and the system It is as if it is a spring that connects the part of the crankshaft in front of the bottle with the 7rai wheel. They are treated like animals. In that case, this system determines the natural frequency of its torsional vibrations two masses connected by an elastic connector (bin) with a torsional spring rate of (crankshaft and flywheel). In that case, this The system consists of harmonic frequencies that fall within the operating range of the engine (in revolutions per minute), and v combines with other frequencies in such a way that it creates stress and is possibly destructive. The I4 sum frequency is determined and analyzed. Since such frequencies are discovered, the damper is used to dampen or reduce vibrations by dissipating energy. It is designed to be mounted on the end of the crankshaft farthest from the eel.
以上のようなアプローチは幾らかの成功を収めているが、この技術を採用してい る市販のエンジンや車輪で証明されるごとく、広範囲の運転速度を有し、従って 広範囲の恐らく危険な運転状態に出会うエンジンにこの技術を応用しようとして 大きな困難を経験してきた。Although these approaches have met with some success, the technology has not yet been adopted. have a wide range of operating speeds, as evidenced by commercially available engines and wheels, and therefore In an effort to apply this technology to engines that encounter a wide range of potentially dangerous operating conditions, I have experienced great difficulties.
発明の詳細な説明 叙上の事実を念頭においたので、本発明の目的はねじり振動を考慮してフライホ イールをクランク軸から効果的に隔離することによって回転クランク軸/フライ ホイール系におけるねじり振動の破壊的応力を回避することにある。Detailed description of the invention With the above facts in mind, it is an object of the present invention to develop a flywheel with consideration to torsional vibration. Rotating crankshaft/fly by effectively isolating the eel from the crankshaft The aim is to avoid the destructive stress of torsional vibrations in the wheel system.
本発明の目的を実現するに当り、フライホイールおよびクランク軸は構成要素間 の角運動をw4ail、在来のクランク軸/7ライホイール系のねじりばね率に 比べて比較的低いねじりばね率を有する弾性継手装置によって連結されている。In realizing the objectives of the invention, the flywheel and crankshaft are The angular movement of w4ail, the torsion spring rate of the conventional crankshaft/7raiwheel system The connection is by an elastic coupling device with a relatively low torsional spring rate.
本発明のさらに別の目的は叙上のごときクランク軸/7ライホイール系を有する エンジンに応力が損傷を与える可能性を、毎分当り回転数に換算してエンジンの 正常運転範囲よりずっと少ない振動数に系のねじり振動の自然振動数を減少させ ることによって、少なくすることにある。本発明のこの目的を達成する場合、上 記の継手によってクランク軸およびフライホイールを分離することとこの継手に 対するはね率を選択することとによってエンジンの正常運転範囲においてねじり 振動の作用を実質的に除去するように振動数を選ぶことができる。Still another object of the present invention is to have a crankshaft/7-wheel system as described above. The probability that stress will cause damage to the engine is calculated in terms of revolutions per minute. Reduces the natural frequency of torsional vibration of the system to a frequency much lower than the normal operating range. By doing so, we aim to reduce it. In achieving this object of the invention, the above The crankshaft and flywheel can be separated by the joint shown below, and this joint torsion within the normal operating range of the engine by selecting a spring rate for The frequency can be chosen to substantially eliminate the effects of vibration.
図面の簡単な説明 本発明の目的のいくつかを以上に述べたが、その他の目的は添付の内面を参考に 詔こなう説明が進むにつれて明白になろう。Brief description of the drawing Although some of the objects of the present invention have been described above, other objects can be understood with reference to the attached contents. This will become clearer as the explanation progresses.
第1囚は本発明を示す多シリンダ内燃機関の構成要素の正面図、第2図は第1図 の装置に用いられた継手要素の拡大正面図、第3図は第2図の要素の斜視図、第 4図は第1−の構成要素の若干を、一部断面で示す拡大正面図である。The first figure is a front view of the components of a multi-cylinder internal combustion engine showing the present invention, and the second figure is the first figure. FIG. 3 is an enlarged front view of the coupling element used in the device shown in FIG. FIG. 4 is an enlarged front view showing some of the first component in cross section.
発明の詳細な説明 本発明はその好ましき実施例を示す添付の図面を参考に以下にさらに詳しく説明 されるが、画業技術者はここに記載の本発明を改変してさらに好ましき発明成果 が得られることを以下の説明に当り先ず理解されたい。従って、以下の説明は画 業技術者向けの広範囲な教示であって本発明に限定されるものてないこととして 理解されたい。Detailed description of the invention The invention will be described in more detail below with reference to the accompanying drawings, which illustrate preferred embodiments thereof. However, art engineers can modify the present invention described herein to obtain further preferable invention results. In the following explanation, it should first be understood that the following can be obtained. Therefore, the following explanation As a comprehensive teaching for industrial engineers and not limited to the present invention, I want to be understood.
さて、添付の図についてさらに詳しく述べると、多シリンダ内燃機関は熟練の機 械技術者には公知のごとくエンジンを作動させるために協同する多数の要素を備 えている。Now, to elaborate further on the attached diagram, a multi-cylinder internal combustion engine As mechanical engineers know, an engine has a number of elements that work together to make it work. It is growing.
図を簡単にするために、ただ若干の要素のみを示すかまたは提案し、明確化のた めにおこなった単純化を理解子ることは技術者の知識次第である。本発明にとっ て重要な要素は第1図に符号10で全体を示したクランク軸と符号11で全体を 示したフライホイールである。従来は、フライホイールはクラッチ、伝動装置、 およびスタータ(以上いずれも図示せず)に近くベルト駆動のクォータポンプお よびファンなどの付属品からは遠いクランク軸の端に取付けられている。In order to simplify the diagram, only a few elements are shown or suggested and for clarity purposes only a few elements are shown or suggested. It is up to the engineer's knowledge to understand the simplifications made. For the present invention The important elements are the crankshaft, indicated as a whole by numeral 10 in Fig. 1, and the crankshaft, indicated as a whole by numeral 11. This is the flywheel shown. Traditionally, the flywheel was used as a clutch, transmission device, and a belt-driven quarter pump near the starter (none of which are shown). It is mounted on the end of the crankshaft far from accessories such as the engine and fans.
多くの在来エンジン、特にレース用自動車、船舶や航空機用に用いられる高性能 エンジンにおいては、フライホイールはエンジンをスタータやクラッチと係合さ せる以上の有用な目的には殆ど役立っていない。慣性質量を出すことに関してフ ライホイールを有するもっと多くの従来の理由は全く関係ない。しかし、慣性質 量の存在がおこす問題、特にねじり振動の作用に関する問題は依然残る。さらに 、エネルギを吸収するのにダンパの使用に依存する公知の上記アプローチではエ ンジンの大きな失敗を回避することはできない。本発明はそのような分野におい て成功であるのみならずもつと汎用性の高い上記に替るものを提供する。High performance used in many conventional engines, especially racing cars, ships and aircraft In an engine, the flywheel connects the engine to the starter and clutch. It serves little useful purpose beyond making a difference. Regarding the production of inertial mass, The more conventional reasons for having a lie wheel are completely irrelevant. However, inertia Problems caused by the presence of quantities, especially regarding the effects of torsional vibrations, remain. moreover , the known above approaches that rely on the use of dampers to absorb energy It is impossible to avoid major engine failures. The present invention is applicable to such fields. We provide an alternative to the above that is not only successful but also highly versatile.
さらに詳しく述べると、回転クランク軸10と回転フライホイール11とを有す る多シリンダ内燃機関において、本発明の改良はクランク軸10と7ライホイー ル11とを結合してフライホイールをクランク軸と共に回転させるためクランク 軸10とフライホイール11(82図乃至第4図)との間に弁筺された全体を符 号12において示す弾性継手装置を提供することによってねじり振動に因る応力 がクランク軸に及ぼす破壊作用を回避することを容易にする。More specifically, it has a rotating crankshaft 10 and a rotating flywheel 11. In a multi-cylinder internal combustion engine, the improvement of the present invention is applicable to the crankshaft 10 and the 7 life wheel. 11 to rotate the flywheel together with the crankshaft. The entire valve housing between the shaft 10 and the flywheel 11 (Figures 82 to 4) is marked. By providing the elastic joint device shown in No. 12, stress caused by torsional vibration can be reduced. makes it easier to avoid destructive effects on the crankshaft.
本発明の重要な%徴によれば、弾性継手装置はねじり振動を考慮するためクラン ク軸の回転慣性からフライホイールを隔離するのに有効な低いねじりばね率を有 する。特に、継手装置はクランク軸と7ライホイールとの間に作動可能に配置さ れかつクランク軸と7ライホイールが限定する回転装置のねじり振動の自然振動 数を所定の低振動数に減少させるのに有効な低ねじりばね率を有する弾性材料、 好ましくはゴムなどのエラストーマよりなる環の形を取っている。本発明の一作 動実施例において、この弾性材料の環は200001n−1b/ radian 以下のねじりばね率を有し、クランク軸およびフライホイールが限定する回転装 置のねじり振動の自然振動数を50馳以下の振動数に減少させる効果がある。According to an important feature of the present invention, the elastic joint device is clamped to account for torsional vibrations. It has a low torsional spring rate that is effective in isolating the flywheel from the rotational inertia of the shaft. do. In particular, the coupling device is operably disposed between the crankshaft and the seven-wheel. Natural vibration of torsional vibration of the rotating device limited by the rekatsu crankshaft and 7-wheel an elastic material having a low torsional spring rate effective to reduce the number of vibrations to a predetermined low frequency; Preferably, it takes the form of a ring made of elastomer such as rubber. A work of this invention In a dynamic embodiment, this ring of elastic material has a diameter of 200001n-1b/radian. Rotating equipment limited by the crankshaft and flywheel with the following torsion spring rate: It has the effect of reducing the natural frequency of torsional vibration of the machine to a frequency of 50 degrees or less.
クランク軸とフライホイールの連結を達成するため、クランク軸とフライホイー ルにはこの両者の連結を可能にすると共に両者間の相対回転を調整する装置が設 けられている。クランク軸10は駆動7ランジ14およびベヤリング面15を限 定する装置を有し、またフライホイール11はクランク軸のベヤリング面と係合 するためのベヤリング16を限定する装置を有する。クランク軸10およびフラ イホイール11の両者は多数のラグを有し、クランク軸はクランク軸の回転軸を 取巻く所定位置に駆動7ランジから延びる多数の駆動ラグ18を有し、フライホ イールはフライホイールの回転軸を取巻く所定位置に7ライホイールから延びる 多数の被動ラグ19を有する。弾性材料の環はベヤリング面15およびベヤリン グ16を取巻き、駆動7ランジ14と7ライホイール11で囲まれている。環ま たは継手装置12はラグ18.19にきちんとはまるように寸法法めされた多数 の開口または穴を有する。従って、ベヤリング面およびベヤリングと継手装置1 2によりつくられる弾性連結とによって、フライホイールおよびクランク軸は相 互に駆動関係にある一方において継手装置のばね力に抗して両者間に実質的な程 度の相対回転を可能にしている。To achieve the connection between the crankshaft and flywheel, the crankshaft and flywheel The wheel is equipped with a device that enables the connection of the two and adjusts the relative rotation between the two. I'm being kicked. The crankshaft 10 limits the drive 7 flange 14 and the bearing surface 15. The flywheel 11 engages with the bearing surface of the crankshaft. It has a device for defining the bearing 16 for this purpose. Crankshaft 10 and flap Both of the wheels 11 have a large number of lugs, and the crankshaft has a rotation axis of the crankshaft. The flywheel has a number of drive lugs 18 extending from the drive 7 langes in predetermined positions surrounding the flywheel. The eel extends from the flywheel to a predetermined position surrounding the axis of rotation of the flywheel. It has a large number of driven lugs 19. The ring of elastic material connects the bearing surface 15 and the bearing The drive wheel 16 is surrounded by a drive wheel 14 and a drive wheel 11. Ringma or the coupling device 12 is a multi-piece sized to fit snugly into the lugs 18.19. having an opening or hole. Therefore, the bearing surface and the bearing and coupling device 1 The flywheel and crankshaft are connected to each other by the elastic connection created by 2. On one side in a driving relationship, there is a substantial distance between the two against the spring force of the coupling device. Allows relative rotation of degrees.
操作について述べると、スタータが7ライホイールに係合することによってエン ジンが始動し駆動力が負荷に伝達されるのを調節するだけの十分な硬さを有する 。しかし、継手装置は十分な弾性を有するので、ねじり振動を考慮しての回転装 置の分析はクランク軸の全体として考えられる慣性質量がフライホイールの全体 として考えられる慣性質量に、従来の場合より著しく低いねじりばね率を有する 構成要素を介して、連結されているという論拠で進められる。In terms of operation, the starter engages with the 7-line wheel to turn the engine on. Sufficient stiffness to regulate engine starting and transfer of drive power to load . However, since the coupling device has sufficient elasticity, it is difficult to use rotating equipment in consideration of torsional vibration. In the analysis of the position, the inertial mass considered as the entire crankshaft is the entire flywheel. The inertial mass considered as having a significantly lower torsional spring rate than the conventional case The argument is that they are connected through their constituent elements.
従って、ねじり振動の自然振動数はねじり振動子とばね率の二つの質量の慣性モ ーメントの公知の要因であって、この要因によりねじり振動子とばね率とが連結 される(慣性モーメントの和にばね率を掛けた積を慣性モーメントの積で割るこ とによって決定される値の平方根に等しい)ので、はね率を減少させることは自 然振動数を減少させ、エンジンの運転範囲以下の範囲まで自然振動数を低減させ ることを効果的に達成する。例えば、50H2以下の自然振動数は3000rp m以下のエンジン速度に相当し、この速度は本発明が利用される多くのエンジン の運転速度以下である。Therefore, the natural frequency of torsional vibration is the inertial modulus of the two masses: the torsional oscillator and the spring rate. This is a well-known factor in the (The product of the sum of the moments of inertia multiplied by the spring rate is divided by the product of the moments of inertia.) is equal to the square root of the value determined by ), so it is natural to reduce the bounce rate. reduce the natural frequency to a range below the engine operating range. effectively accomplish the following. For example, the natural frequency below 50H2 is 3000rp m, which corresponds to an engine speed of less than operating speed or less.
逆に、クランク軸/フライホイール系の自然振動数を制御する能力は他の形式、 寸法および範囲のエンジンに本発明の教示を適応させる可能性を開く。Conversely, the ability to control the natural frequency of the crankshaft/flywheel system is Opens up the possibility of adapting the teachings of the invention to engines of size and range.
使用について述べると、ねじり振動を考慮するためフライホイールをクランク軸 から隔離することと以上に述べた装置とによって7ライホイールのクランク軸に 対する回転は、これら両要素の回転位置間の偏倚運動また角度的相違が、伝達さ れる力および使用される特定のばね定数の如何により、数置ですむような方法で 、可能である。このような偏倚運動は、本発明においては、回転系が本発明によ らなければ起る恐れのあるねじり振動の悪影響から適正に防′謹されることを保 証するものとして有利であって、不利とはみなされない。In terms of use, the flywheel is attached to the crankshaft to account for torsional vibrations. By isolating it from the Rotation with respect to the depending on the force applied and the specific spring constant used, in such a way that only a few positions are required. , is possible. In the present invention, such a biasing motion is realized when the rotating system according to the present invention Ensure adequate protection from the adverse effects of torsional vibration that may otherwise occur. It is advantageous as evidence and is not considered disadvantageous.
図面および明細誉において、本発明の好ましき実施例を説明した。しかして特定 の用語を使用したが、説明に用いられた用語は一般的説明的意味においてのみ用 いたもので、制限を意図したものではない。Preferred embodiments of the invention have been described in the drawings and specification. However, specific terms used in the explanation, but the terms used in the explanation are to be used only in a general descriptive sense. It is not intended to be limiting.
国際調査報告 I鴎−豐一−^鉾市ロー”v PCT/1ls8610178フ1m#’m1 16MIAl1m<AboIITla、PCT/US861017B?international search report I-Fuichi-^Hoko City Low”v PCT/1ls8610178fu1m#’m1 16MIAl1m<AboIITla, PCT/US861017B?
Claims (14)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US1986/001787 WO1988001703A1 (en) | 1986-08-29 | 1986-08-29 | Torsional vibration isolator and method |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH02502303A true JPH02502303A (en) | 1990-07-26 |
Family
ID=22195620
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP61504795A Pending JPH02502303A (en) | 1986-08-29 | 1986-08-29 | Torsional vibration isolation device and method |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0280679A4 (en) |
JP (1) | JPH02502303A (en) |
KR (1) | KR880701842A (en) |
WO (1) | WO1988001703A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3821022A1 (en) * | 1988-06-22 | 1989-12-28 | Bosch Gmbh Robert | DAMPING DEVICE FOR A GEAR SHAFT |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1290551A (en) * | 1917-07-17 | 1919-01-07 | Edward John Hardy | Universal joint. |
US1701518A (en) * | 1925-12-04 | 1929-02-12 | Chandler Motor Car Company | Vibration-damping flywheel |
US1925074A (en) * | 1928-07-19 | 1933-08-29 | Packard Motor Car Co | Vibration damper for explosion motors |
US1939855A (en) * | 1930-05-03 | 1933-12-19 | Continental Motors Corp | Engine |
US1978199A (en) * | 1931-12-04 | 1934-10-23 | Continental Motors Corp | Vibration damper |
GB580901A (en) * | 1944-09-15 | 1946-09-24 | Dunlop Rubber Co | Improvements in or relating to shaft couplings |
US2724377A (en) * | 1952-04-22 | 1955-11-22 | Daimler Benz Ag | Driving device for accessory shafts |
US2679148A (en) * | 1952-09-22 | 1954-05-25 | H A Thrush & Company | Flexible coupling |
US3793894A (en) * | 1970-06-26 | 1974-02-26 | Litton Business Systems Inc | Mechanical mechanism |
US3995513A (en) * | 1975-03-03 | 1976-12-07 | Caterpillar Tractor Co. | Drive line vibration absorber |
DE2534684C2 (en) * | 1975-08-02 | 1982-08-26 | Daimler-Benz Ag, 7000 Stuttgart | Device for vibration damping in the drive train of vehicles |
DE2709959A1 (en) * | 1977-03-08 | 1978-09-14 | Daimler Benz Ag | Cardan shaft coupling for vehicle - has interdigitated driving and driven members engaged in pockets in flat section resilient ring |
DE3038847A1 (en) * | 1980-10-15 | 1982-05-27 | Bayerische Motoren Werke AG, 8000 München | FLYWHEEL BEARING FOR INTERNAL COMBUSTION ENGINES |
US4617884A (en) * | 1984-07-27 | 1986-10-21 | Charles A. Allen | Torsional vibration isolator and method |
-
1986
- 1986-08-29 WO PCT/US1986/001787 patent/WO1988001703A1/en not_active Application Discontinuation
- 1986-08-29 JP JP61504795A patent/JPH02502303A/en active Pending
- 1986-08-29 EP EP19860905596 patent/EP0280679A4/en not_active Withdrawn
-
1988
- 1988-04-15 KR KR1019880700401A patent/KR880701842A/en not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
EP0280679A1 (en) | 1988-09-07 |
EP0280679A4 (en) | 1990-01-08 |
WO1988001703A1 (en) | 1988-03-10 |
KR880701842A (en) | 1988-11-05 |
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