JPH0814332A - Torque fluctuation absorbing damper - Google Patents
Torque fluctuation absorbing damperInfo
- Publication number
- JPH0814332A JPH0814332A JP16482594A JP16482594A JPH0814332A JP H0814332 A JPH0814332 A JP H0814332A JP 16482594 A JP16482594 A JP 16482594A JP 16482594 A JP16482594 A JP 16482594A JP H0814332 A JPH0814332 A JP H0814332A
- Authority
- JP
- Japan
- Prior art keywords
- pulley
- hub
- torsional
- elastomer member
- torque fluctuation
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
- F16F15/167—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material having an inertia member, e.g. ring
-
- 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
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
-
- 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
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
- F16H2055/366—Pulleys with means providing resilience or vibration damping
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Pulleys (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、エンジンのクランクシ
ャフトの動力を各種補器へ伝達する際に、エンジンの各
行程による前記クランクシャフトの伝達トルクの変動を
吸収絶縁するトルク変動吸収ダンパに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torque fluctuation absorbing damper that absorbs and isolates fluctuations in the torque transmitted by the crankshaft during each stroke of the engine when transmitting the power of the crankshaft of the engine to various auxiliary devices.
【０００２】[0002]
【従来の技術】従来、この種のトルク変動吸収ダンパ
は、基本的には図２に示すように、エンジンのクランク
シャフトの先端に取り付けられるハブ１０１の外周に、
ベアリング１０２ａを介して捩り変位（軸周り方向の変
位）自在に同心配置されたプーリ１０２ｂを、エラスト
マ部材１０２ｃを介して連結した構造のカップリング部
１０２を有する（例えば実開昭６３−６８５４０号公報
参照）。すなわちクランクシャフトの動力の一部は、プ
ーリ１０２ｂに巻架された図示されていない無端ベルト
を介して例えばオルタネータやコンプレッサ等の各種補
器に与えられるが、クランクシャフトはエンジンの各行
程によるトルク変動を伴って回転されるため、カップリ
ング部１０２は、このトルク変動をプーリとの間でエラ
ストマ部材１０２ｃの捩り変形作用によって吸収絶縁
し、プーリ１０２ｂからの伝達トルクの平滑化を図るも
のである。2. Description of the Related Art Conventionally, a torque fluctuation absorbing damper of this type is basically arranged on the outer periphery of a hub 101 attached to the tip of a crankshaft of an engine, as shown in FIG.
It has a coupling portion 102 having a structure in which pulleys 102b concentrically arranged so as to be torsionally displaced (displacement in the axial direction) via bearings 102a are connected via an elastomer member 102c (for example, Japanese Utility Model Laid-Open No. Sho 63-68540). reference). That is, a part of the power of the crankshaft is given to various auxiliary devices such as an alternator and a compressor via an endless belt (not shown) wound around the pulley 102b, but the crankshaft changes torque due to each stroke of the engine. Therefore, the coupling portion 102 absorbs and insulates this torque fluctuation with the pulley by the torsional deformation action of the elastomer member 102c, and smoothes the torque transmitted from the pulley 102b.
【０００３】また、前記ハブ１０１の外周には、別のエ
ラストマ部材１０３ａを介して環状質量体１０３ｂを弾
性的に連結した構造のトーショナルダンパ部１０３が並
設されている。このトーショナルダンパ部１０３は、所
定の振動数域においてクランクシャフトの捩り振動を打
ち消すように共振し、クランクシャフトの捩り振動自体
を低減する制振機能を発揮するものである。Further, on the outer periphery of the hub 101, a torsion damper portion 103 having a structure in which an annular mass body 103b is elastically connected via another elastomer member 103a is provided in parallel. The torsional damper section 103 resonates so as to cancel the torsional vibration of the crankshaft in a predetermined frequency range, and exhibits a vibration damping function of reducing the torsional vibration of the crankshaft itself.
【０００４】ところで、カップリング部１０２における
捩り方向固有振動数は、プーリ１０２ｂの慣性質量が大
きいこと及びエラストマ部材１０２ｃがトーショナルダ
ンパ部１０３のエラストマ部材１０３ａよりばね定数が
低いことなどから、トーショナルダンパ部１０３の捩り
方向固有振動数に比較してかなり低いものとなってお
り、例えばアイドル回転時におけるクランクシャフトの
トルク変動の周波数以下の領域にあるため、エンジン始
動時に、アイドリングに至る過程で、クランクシャフト
のトルク変動の周波数がカップリング部１０２の捩り方
向固有振動数域を通過することになる。そして、このと
きのカップリング部１０２の共振によって、ハブ１０１
に対してプーリ１０２ｂが捩り方向へ大きく振動変位さ
れると、エラストマ部材１０２ｃが過大変形を受けて破
損を来す恐れがあることから、通常、ハブ１０１とプー
リ１０２ｂの捩り方向相対変位量を制限するストッパ１
０４が設けられている。このストッパ１０４は、図３に
も示すように、ハブ１０１側に固定されて外周に凹凸を
有する金属リング１０４ａと、プーリ１０２ｂ側に固定
されて内周に前記凹凸と遊嵌される凹凸を有する金属リ
ング１０４ｂとからなる。The torsional natural frequency in the coupling portion 102 is torsional because the inertial mass of the pulley 102b is large and the elastomer member 102c has a lower spring constant than the elastomer member 103a of the torsional damper portion 103. It is considerably lower than the natural frequency of the damper portion 103 in the torsional direction, for example, in the region below the frequency of torque fluctuation of the crankshaft during idle rotation, so during idling during engine startup, The frequency of torque fluctuation of the crankshaft passes through the torsional natural frequency range of the coupling portion 102. Then, due to the resonance of the coupling portion 102 at this time, the hub 101
On the other hand, when the pulley 102b is largely vibrated and displaced in the torsional direction, the elastomer member 102c may be excessively deformed and may be damaged. Therefore, the relative displacement of the hub 101 and the pulley 102b in the torsional direction is usually limited. Stopper 1
04 are provided. As shown in FIG. 3, the stopper 104 has a metal ring 104a that is fixed to the hub 101 side and has unevenness on the outer circumference, and a metal ring 104a that is fixed to the pulley 102b side and that is loosely fitted to the unevenness on the inner circumference. The metal ring 104b.
【０００５】[0005]
【発明が解決しようとする課題】上記従来のトルク変動
吸収ダンパによれば、カップリング部１０２の共振によ
るプーリ１０２ｂの振動変位量、言い換えればエラスト
マ部材１０２ｃの捩り変形量を、ストッパ１０４におけ
る金属リング１０４ａ，１０４ｂの凹凸同士の干渉によ
って所定範囲に制限しているため、共振時に金属による
打音を発生する問題が指摘される。According to the conventional torque fluctuation absorbing damper described above, the vibration displacement amount of the pulley 102b due to the resonance of the coupling portion 102, in other words, the torsional deformation amount of the elastomer member 102c, is set to the metal ring of the stopper 104. It is pointed out that a metal tapping sound is generated at the time of resonance because the predetermined range is limited by the interference between the irregularities of 104a and 104b.
【０００６】本発明は、上記のような事情のもとになさ
れたもので、その主な技術的課題とするところは、カッ
プリング部の共振時に打音を発生することなくエラスト
マ部材の過大変形を有効に防止することにある。The present invention has been made under the above circumstances, and its main technical problem is that the elastomer member is excessively deformed without generating a tapping sound at the time of resonance of the coupling portion. Is to effectively prevent.
【０００７】[0007]
【課題を解決するための手段】上述した技術的課題は、
本発明によって有効に解決することができる。すなわち
本発明に係るトルク変動吸収ダンパは、エンジンのクラ
ンクシャフトに取り付けられるハブの外周に第一のエラ
ストマ部材を介してプーリを捩り変位自在に連結したカ
ップリング部と、前記ハブの外周に前記第一のエラスト
マ部材と軸方向に並んだ第二のエラストマ部材を介して
環状質量体を捩り変位自在に連結した構造であって前記
カップリング部と異なる固有振動数を有するトーショナ
ルダンパ部と、前記プーリ側とトーショナルダンパ部と
の間に形成された隙間に封入された粘性流体とを備え
る。本発明において一層好ましくは、前記隙間が、プー
リの内周面に密接嵌着されトーショナルダンパ部の側面
に沿って径方向に延在された仕切板と、この仕切板の内
径とハブとの間に摺動自在に介在されたシール部材とに
よって形成される。また、前記隙間が、プーリの内周面
と環状質量体の外周面との間の滑りベアリングの介在部
分に連通される。The above-mentioned technical problems are as follows.
The present invention can effectively solve the problem. That is, the torque fluctuation absorbing damper according to the present invention includes a coupling portion in which a pulley is torsionally displaceably connected to the outer circumference of a hub attached to a crankshaft of an engine via a first elastomer member, and the first outer circumference of the hub is provided with the coupling portion. And a torsional damper part having a natural frequency different from that of the coupling part, which has a structure in which an annular mass body is connected in a torsionally displaceable manner via a second elastomer member arranged in an axial direction with one elastomer member, and And a viscous fluid sealed in a gap formed between the pulley side and the torsional damper portion. In the present invention, more preferably, the gap is a partition plate that is closely fitted to the inner peripheral surface of the pulley and extends in the radial direction along the side surface of the torsional damper portion, and the inner diameter of the partition plate and the hub. And a seal member slidably interposed therebetween. Further, the gap is communicated with an intervening portion of the slide bearing between the inner peripheral surface of the pulley and the outer peripheral surface of the annular mass body.
【０００８】[0008]
【作用】カップリング部が捩り方向に共振した時のプー
リの振動変位量の増大は、反復的に捩り変位されるプー
リ側と、前記カップリング部の共振振動数では共振しな
いトーショナルダンパ部との間の隙間内で剪断を受ける
粘性流体の粘性抵抗によるダンピング作用によって抑え
られる。特に、プーリの内周面に密接嵌合されトーショ
ナルダンパ部の側面に沿ってハブ側へ径方向に延在され
た仕切板と、この仕切板の内径とハブとの間に摺動自在
に介在されたシール部材とによって、前記隙間の両側で
捩り方向へ相対変位される面間の距離を小さくすると共
に、粘性流体との摩擦面積を大きくし、粘性ダンピング
による制動作用を高めることができる。また、プーリを
トーショナルダンパ部の環状質量体の外周に同心的に支
持する滑りベアリングの介在部分に、前記隙間を連通さ
せることによって、この滑りベアリングが潤滑される。When the coupling portion resonates in the torsional direction, the amount of vibration displacement of the pulley is increased by the pulley side which is repeatedly torsionally displaced and the torsional damper portion which does not resonate at the resonance frequency of the coupling portion. It is suppressed by the damping action due to the viscous resistance of the viscous fluid that is sheared in the gap between them. In particular, a partition plate that is closely fitted to the inner peripheral surface of the pulley and extends radially toward the hub along the side surface of the torsional damper, and is slidable between the inner diameter of this partition plate and the hub. The intervening sealing member can reduce the distance between the surfaces relatively displaced in the torsional direction on both sides of the gap, increase the friction area with the viscous fluid, and enhance the braking action by viscous damping. Further, the sliding bearing is lubricated by communicating the gap with an intervening portion of the sliding bearing that concentrically supports the pulley on the outer circumference of the annular mass body of the torsional damper portion.
【０００９】また、トーショナルダンパ部の共振時はカ
ップリング部は共振しないから、トーショナルダンパ部
の共振によるクランクシャフトの捩り振動減衰において
も、このトーショナルダンパ部における第二のエラスト
マ部材の内部摩擦によるダンピングに加えて、カップリ
ング部のプーリ側とこれに対して相対的に捩り変位され
るトーショナルダンパ部との間で粘性流体が剪断を受け
ることによって発生する粘性抵抗によるダンピングが得
られる。Further, since the coupling portion does not resonate when the torsional damper portion resonates, even when torsional vibration of the crankshaft is attenuated by the resonance of the torsional damper portion, the inside of the second elastomer member in the torsional damper portion is also reduced. In addition to frictional damping, damping due to viscous resistance generated by shearing of viscous fluid between the pulley side of the coupling section and the torsional damper section that is torsionally displaced relative to this is obtained. .
【００１０】[0010]
【実施例】図１は、本発明に係るトルク変動吸収ダンパ
の一実施例を、その軸心を通る平面で切断して示すもの
で、参照符号１はエンジンのクランクシャフトの軸端に
取り付けられるハブである。このハブ１の外周には、第
一のエラストマ部材２１を介してプーリ２２を捩り変位
自在に連結したカップリング部２と、第二のエラストマ
部材３１を介して環状質量体３２を捩り変位自在に連結
した構造のトーショナルダンパ部３が設けられている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows an embodiment of a torque fluctuation absorbing damper according to the present invention by cutting it along a plane passing through its axis. Reference numeral 1 is attached to an axial end of a crankshaft of an engine. It's a hub. On the outer periphery of the hub 1, a coupling portion 2 in which a pulley 22 is torsionally displaceable connected via a first elastomer member 21 and an annular mass body 32 is torsionally displaceable via a second elastomer member 31. A torsional damper portion 3 having a connected structure is provided.
【００１１】ハブ１は、クランクシャフトへの取付部で
ある径方向部１１及びその外径から延在された外径筒状
部１２を有する断面略Ｌ字形を呈する。プーリ２２の外
周面には大径のＶプーリ溝２２ａ及び小径のＶプーリ溝
２２ｂが形成されており、プーリ２２の内周面もこれに
対応して、Ｖプーリ溝２２ａ側が大径、他方のＶプーリ
溝２２ｂ側が小径となる段差状に形成されている。第一
のエラストマ部材２１は、ハブ１の外径筒状部１２にお
ける径方向部１１寄りの外周面に嵌着されたスリーブ２
３と、プーリ２２のＶプーリ溝２２ａ側の大径内周面に
嵌着されたスリーブ２４との間に一体に加硫成形されて
いる。環状質量体３２は、プーリ２２の小径のＶプーリ
溝２２ｂ側の内周に配置されており、第二のエラストマ
部材３１は、ハブ１の外径筒状部１２における径方向部
１１と反対側の端部寄りの外周面に嵌着されたスリーブ
３３と、環状質量体３２との間に一体に加硫成形されて
いる。また、環状質量体３２とプーリ２２との対向周面
間には、合成樹脂材からなる滑りベアリング４が摺動自
在に介在されている。The hub 1 has a substantially L-shaped cross section having a radial portion 11 which is a mounting portion to a crankshaft and an outer diameter cylindrical portion 12 extending from the outer diameter thereof. A large-diameter V pulley groove 22a and a small-diameter V pulley groove 22b are formed on the outer peripheral surface of the pulley 22, and the inner peripheral surface of the pulley 22 correspondingly has a large diameter on the V pulley groove 22a side and the other side. The V pulley groove 22b side is formed in a stepped shape having a small diameter. The first elastomer member 21 is a sleeve 2 fitted to the outer peripheral surface of the outer diameter tubular portion 12 of the hub 1 near the radial portion 11.
3 and the sleeve 24 fitted to the large-diameter inner peripheral surface of the pulley 22 on the V pulley groove 22a side are integrally vulcanized and molded. The annular mass body 32 is arranged on the inner periphery of the pulley 22 on the side of the small-diameter V-pulley groove 22b, and the second elastomer member 31 is provided on the opposite side of the outer diameter tubular portion 12 of the hub 1 from the radial portion 11. It is integrally vulcanized and molded between a sleeve 33 fitted to the outer peripheral surface near the end of the and the annular mass body 32. Further, a slide bearing 4 made of a synthetic resin material is slidably interposed between the opposed peripheral surfaces of the annular mass body 32 and the pulley 22.
【００１２】ハブ１とプーリ２２の間であって第一のエ
ラストマ部材２１とトーショナルダンパ部３の間には、
このトーショナルダンパ部３における環状質量体３２及
び第二のエラストマ部材３１の内側面（第一のエラスト
マ部材２１側の面）に近接して径方向に延びる仕切板５
が配置され、その外径端部がプーリ２２の内周面に密接
嵌着されている。この仕切板５の内径端部とハブ１の外
径筒状部１２との間には円周方向摺動自在なシール部材
６が介在されている。前記環状質量体３２の外径部に
は、プーリ２２の内周面に形成された径方向段差面２２
ｃと前記仕切板５との間を外径側へ延びる鍔部３２ａが
形成されている。Between the hub 1 and the pulley 22 and between the first elastomer member 21 and the torsional damper portion 3,
The partition plate 5 extending radially in proximity to the inner surface of the annular mass body 32 and the second elastomer member 31 (the surface on the side of the first elastomer member 21) of the torsion damper portion 3.
Is disposed, and the outer diameter end portion is closely fitted to the inner peripheral surface of the pulley 22. A circumferentially slidable seal member 6 is interposed between the inner diameter end of the partition plate 5 and the outer diameter cylindrical portion 12 of the hub 1. A radial step surface 22 formed on the inner peripheral surface of the pulley 22 is provided on the outer diameter portion of the annular mass body 32.
A flange portion 32a extending between the c and the partition plate 5 toward the outer diameter side is formed.
【００１３】プーリ２２側とトーショナルダンパ部３と
の間、更に詳しくはプーリ２２の内周面における径方向
段差面２２ｃ、プーリ２２の大径側内周面に密接嵌着さ
れた仕切板５及びその内径端とハブ１との間を密封する
シール部材６と、鍔部３２ａを含む環状質量体３２及び
第二のエラストマ部材３１との間には、粘性流体８が封
入された狭い隙間７が形成されている。この隙間７の一
端は、滑りベアリング４の介在部分に連通しており、こ
の滑りベアリング４の外側は、プーリ２２の小径内周面
に嵌着されて環状質量体３２の外周面に摺動自在に密接
したオイルシール９で密封されている。Between the pulley 22 side and the torsional damper portion 3, more specifically, the radial step surface 22c on the inner peripheral surface of the pulley 22 and the partition plate 5 closely fitted to the large diameter inner peripheral surface of the pulley 22. A narrow gap 7 in which the viscous fluid 8 is sealed is provided between the seal member 6 for sealing between the inner diameter end and the hub 1, the annular mass body 32 including the flange portion 32a, and the second elastomer member 31. Are formed. One end of the gap 7 communicates with an intervening portion of the slide bearing 4, and the outside of the slide bearing 4 is fitted to the small-diameter inner peripheral surface of the pulley 22 and slidable on the outer peripheral surface of the annular mass body 32. It is sealed with an oil seal 9 which is in close contact with.
【００１４】なお、図中参照符号３２ｂは隙間７への粘
性流体８の注入孔であり、３２ｃは粘性流体８の注入後
に前記注入孔３２ｂを密栓してなる球体である。In the figure, reference numeral 32b is an injection hole for the viscous fluid 8 into the gap 7, and 32c is a sphere formed by tightly plugging the injection hole 32b after the injection of the viscous fluid 8.
【００１５】この実施例によるトルク変動吸収ダンパに
おいて、カップリング部２の捩り方向固有振動数は、先
に述べたように、エンジンのアイドル回転時におけるク
ランクシャフトのトルク変動の周波数以下の領域にある
のに対し、トーショナルダンパ部３は、比較的高速回転
域でのクランクシャフトの捩り振動を共振吸収するもの
であるため、その捩り方向固有振動数がカップリング部
２に比較して高いものとなっている。したがって、エン
ジン始動時に、クランキングからアイドリングに至る過
程で、カップリング部２がクランクシャフトの低周波数
のトルク変動と共振し、ハブ１に対してプーリ２２が捩
り方向へ大きく振動変位されることによって第一のエラ
ストマ部材２１の捩り変位量が増大するが、トーショナ
ルダンパ部３は共振していないから、プーリ２２及びこ
れと一体的に捩り方向へ反復変位される仕切板５との間
で、隙間７内の粘性流体８が剪断を受けることになり、
この時の粘性抵抗によって、プーリ２２の捩り変位の振
幅が抑えられ、第一のエラストマ部材２１の捩り変位量
が制限される。また、トーショナルダンパ部３がクラン
クシャフトの捩り振動を共振吸収する高速回転域では、
カップリング部２は共振しないから、この場合も隙間７
内の粘性流体８が剪断を受けることになり、トーショナ
ルダンパ部３の第二のエラストマ部材３１の内部摩擦に
よるダンピングに加えて、前記粘性流体８の粘性抵抗に
よるダンピングが得られる。In the torque fluctuation absorbing damper according to this embodiment, the natural frequency in the torsional direction of the coupling portion 2 is, as described above, within the frequency range of the torque fluctuation of the crankshaft during engine idle rotation. On the other hand, since the torsional damper section 3 resonantly absorbs the torsional vibration of the crankshaft in a relatively high speed rotation range, its torsional natural frequency is higher than that of the coupling section 2. Has become. Therefore, when the engine is started, during the process from cranking to idling, the coupling portion 2 resonates with the low-frequency torque fluctuation of the crankshaft, and the pulley 22 is largely oscillated and displaced in the torsional direction with respect to the hub 1. Although the torsional displacement amount of the first elastomer member 21 increases, the torsional damper portion 3 does not resonate, so that between the pulley 22 and the partition plate 5 which is integrally displaced repeatedly in the torsional direction, The viscous fluid 8 in the gap 7 will be sheared,
The viscous resistance at this time suppresses the amplitude of the torsional displacement of the pulley 22 and limits the amount of torsional displacement of the first elastomer member 21. Further, in the high-speed rotation range where the torsional damper section 3 absorbs the torsional vibration of the crankshaft by resonance,
Since the coupling part 2 does not resonate, the gap 7
The viscous fluid 8 inside is subjected to shearing, and in addition to the damping due to the internal friction of the second elastomer member 31 of the torsional damper portion 3, damping due to the viscous resistance of the viscous fluid 8 is obtained.
【００１６】粘性流体８が封入された隙間７はその両側
の対向面間の幅が狭く、環状質量体３２に形成された鍔
部３２ａと、その軸方向両側にある仕切板５及びプーリ
２２の径方向段差面２２ｃによって、径方向へ大きく折
り返された形状であるため、粘性流体８との摩擦面が大
きくなっている。したがって、プーリ２２の捩り変位の
振幅を抑えるのに有効な大きな減衰力が得られる。The gap 7 in which the viscous fluid 8 is enclosed has a narrow width between the facing surfaces on both sides thereof, and the collar portion 32a formed on the annular mass body 32 and the partition plate 5 and the pulley 22 on both sides in the axial direction thereof. Since the shape is largely folded back in the radial direction by the radial step surface 22c, the friction surface with the viscous fluid 8 is large. Therefore, a large damping force effective in suppressing the amplitude of the torsional displacement of the pulley 22 can be obtained.
【００１７】合成樹脂からなる滑りベアリング４は、プ
ーリ２２をトーショナルダンパ部３の環状質量体３２の
外周に同心的かつ捩り変位自在に支持するものである
が、通常、この種の滑りベアリング４は摺動によって摩
耗が大きくなりやすい。しかしこの実施例では、滑りベ
アリング４が隙間７に封入された粘性流体８によって潤
滑されるので、摩耗を受けにくく、その耐久性が向上さ
れる。The sliding bearing 4 made of synthetic resin supports the pulley 22 concentrically and torsionally displaceably on the outer periphery of the annular mass body 32 of the torsional damper portion 3. Normally, this type of sliding bearing 4 is used. Wear tends to increase due to sliding. However, in this embodiment, since the plain bearing 4 is lubricated by the viscous fluid 8 sealed in the gap 7, it is less susceptible to wear and its durability is improved.
【００１８】[0018]
【発明の効果】本発明によると、次のような効果が実現
される。 (1) カップリング部が捩り方向に共振した時に粘性流体
の粘性ダンピング作用によってプーリの振動変位量の増
大が抑えられるので、ストッパを設けた場合のような干
渉音を発生することなくカップリング部の第一のエラス
トマ部材の大変形が有効に防止される。 (2) プーリをトーショナルダンパ部の環状質量体の外周
に同心的に支持する滑りベアリングが粘性流体で潤滑さ
れるので、その耐久性が向上する。 (3) 前記粘性流体の粘性ダンピングによって、トーショ
ナルダンパ部による制振力が向上する。According to the present invention, the following effects are realized. (1) When the coupling section resonates in the torsional direction, the viscous damping action of the viscous fluid suppresses the increase in the vibration displacement of the pulley.Therefore, the coupling section does not generate the interfering noise as when a stopper is installed. The large deformation of the first elastomer member is effectively prevented. (2) The sliding bearing that concentrically supports the pulley on the outer circumference of the annular mass body of the torsional damper is lubricated by the viscous fluid, so that its durability is improved. (3) The viscous damping of the viscous fluid improves the vibration damping force of the torsional damper.
【図１】本発明に係るトルク変動吸収ダンパの一実施例
を、その軸心を通る平面で切断して示す半断面図であ
る。FIG. 1 is a half sectional view showing an embodiment of a torque fluctuation absorbing damper according to the present invention, cut along a plane passing through an axis thereof.
【図２】従来のトルク変動吸収ダンパの一例を、その軸
心を通る平面で切断して示す半断面図である。FIG. 2 is a half cross-sectional view showing an example of a conventional torque fluctuation absorbing damper, taken along a plane passing through an axis thereof.
【図３】上記従来例を、図２におけるIII −III 線位置
で切断して示す部分的な断面図である。FIG. 3 is a partial cross-sectional view showing the above conventional example taken along the line III-III in FIG.
１ ハブ １１ 径方向部 １２ 外径筒状部 ２ カップリング部 ２１ 第一のエラストマ部材 ２２ プーリ ２２ａ，２２ｂ Ｖプーリ溝 ２３，２４，３３ スリーブ ３ トーショナルダンパ部 ３１ 第二のエラストマ部材 ３２ 環状質量体 ４ ベアリング ５ 仕切板 ６ シール部材 ７ 隙間 ８ 粘性流体 ９ オイルシール DESCRIPTION OF SYMBOLS 1 hub 11 radial direction portion 12 outer diameter tubular portion 2 coupling portion 21 first elastomer member 22 pulleys 22a, 22b V pulley groove 23, 24, 33 sleeve 3 torsional damper portion 31 second elastomer member 32 annular mass Body 4 Bearing 5 Partition plate 6 Seal member 7 Gap 8 Viscous fluid 9 Oil seal
Claims (3)
られるハブ（１）の外周に第一のエラストマ部材（２
１）を介してプーリ（２２）を捩り変位自在に連結した
カップリング部（２）と、 前記ハブ（１）の外周に前記第一のエラストマ部材（２
１）と軸方向に並んだ第二のエラストマ部材（３１）を
介して環状質量体（３２）を捩り変位自在に連結した構
造であって前記カップリング部（２）と異なる固有振動
数を有するトーショナルダンパ部（３）と、 前記プーリ（２２）側とトーショナルダンパ部（３）と
の間に形成された隙間（７）に封入された粘性流体
（８）と、を備えることを特徴とするトルク変動吸収ダ
ンパ。1. A first elastomer member (2) is provided on the outer periphery of a hub (1) attached to a crankshaft of an engine.
A coupling part (2) in which a pulley (22) is twistably displaced via a (1) and a first elastomer member (2) on the outer circumference of the hub (1).
1) is a structure in which an annular mass body (32) is torsionally displaced via a second elastomer member (31) axially aligned with 1) and has a natural frequency different from that of the coupling portion (2). It is provided with a torsional damper part (3) and a viscous fluid (8) enclosed in a gap (7) formed between the pulley (22) side and the torsional damper part (3). Torque fluctuation absorption damper.
が、 プーリ（２２）の内周面に密接嵌着されトーショナルダ
ンパ部（３）の側面に沿って径方向に延在された仕切板
（５）と、 この仕切板（５）の内径とハブ（１）との間に摺動自在
に介在されたシール部材（６）との間に延在されたこと
を特徴とする請求項１に記載のトルク変動吸収ダンパ。2. A gap (7) enclosing a viscous fluid (8).
Is a partition plate (5) closely fitted to the inner peripheral surface of the pulley (22) and extending in the radial direction along the side surface of the torsional damper part (3), and the inner diameter of the partition plate (5). The torque fluctuation absorbing damper according to claim 1, characterized in that it extends between a hub (1) and a sealing member (6) slidably interposed between the hub and the hub (1).
（３２）の外周面との間に滑りベアリング（４）が介在
され、 粘性流体（８）を封入した隙間（７）が前記滑りベアリ
ング（４）の介在部分に連通していることを特徴とする
請求項１に記載のトルク変動吸収ダンパ。3. A slide bearing (4) is interposed between the inner peripheral surface of the pulley (22) and the outer peripheral surface of the annular mass body (32), and a gap (7) enclosing a viscous fluid (8) is provided. The torque fluctuation absorbing damper according to claim 1, characterized in that it is communicated with an intervening portion of the plain bearing (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16482594A JP3582536B2 (en) | 1994-06-24 | 1994-06-24 | Torque fluctuation absorption damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16482594A JP3582536B2 (en) | 1994-06-24 | 1994-06-24 | Torque fluctuation absorption damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0814332A true JPH0814332A (en) | 1996-01-16 |
| JP3582536B2 JP3582536B2 (en) | 2004-10-27 |
Family
ID=15800640
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16482594A Expired - Fee Related JP3582536B2 (en) | 1994-06-24 | 1994-06-24 | Torque fluctuation absorption damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3582536B2 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10227333A (en) * | 1997-02-14 | 1998-08-25 | Nok Megurasutikku Kk | Dynamic damper |
| EP1146255A3 (en) * | 2000-04-15 | 2003-12-10 | Carl Freudenberg KG | Torsional elastic coupling for belt pulley |
| DE102006016202B3 (en) * | 2006-04-06 | 2007-07-05 | Carl Freudenberg Kg | Belt pulley, has integrated torsional vibration damper, hub ring and flywheel rim surrounding hub ring with first radial distance, whereas first spring body is arranged in first formed crack over first space |
| ITTO20080587A1 (en) * | 2008-07-29 | 2010-01-30 | Dayco Europe Srl | PULLEY PACKAGING MACHINE PREFERIBLY TO DRIVE AN ORGAN ACCESSORY VIA A BELT DRIVE IN AN INTERNAL COMBUSTION ENGINE |
| ITTO20080586A1 (en) * | 2008-07-29 | 2010-01-30 | Dayco Europe Srl | PULLEY PACKAGING MACHINE PREFERIBLY TO DRIVE AN ORGAN ACCESSORY VIA A BELT DRIVE IN AN INTERNAL COMBUSTION ENGINE |
| CN102364158A (en) * | 2011-09-07 | 2012-02-29 | 湖北航天化学技术研究所 | Vibration absorber |
| CN104675899A (en) * | 2015-02-13 | 2015-06-03 | 柳州金鸿橡塑有限公司 | Parallel distribution type double-frequency twisting vibration reducer |
| WO2021094557A1 (en) * | 2019-11-15 | 2021-05-20 | Hasse & Wrede Gmbh | Crankshaft arrangement comprising a torsional vibration damper |
| CN114729674B (en) * | 2019-11-15 | 2024-06-25 | 哈瑟&弗雷德有限公司 | Crankshaft assembly with torsional vibration damper |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101886685A (en) * | 2010-07-19 | 2010-11-17 | 奇瑞汽车股份有限公司 | Vibration damper assembly |
-
1994
- 1994-06-24 JP JP16482594A patent/JP3582536B2/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10227333A (en) * | 1997-02-14 | 1998-08-25 | Nok Megurasutikku Kk | Dynamic damper |
| EP1146255A3 (en) * | 2000-04-15 | 2003-12-10 | Carl Freudenberg KG | Torsional elastic coupling for belt pulley |
| DE102006016202B3 (en) * | 2006-04-06 | 2007-07-05 | Carl Freudenberg Kg | Belt pulley, has integrated torsional vibration damper, hub ring and flywheel rim surrounding hub ring with first radial distance, whereas first spring body is arranged in first formed crack over first space |
| ITTO20080587A1 (en) * | 2008-07-29 | 2010-01-30 | Dayco Europe Srl | PULLEY PACKAGING MACHINE PREFERIBLY TO DRIVE AN ORGAN ACCESSORY VIA A BELT DRIVE IN AN INTERNAL COMBUSTION ENGINE |
| ITTO20080586A1 (en) * | 2008-07-29 | 2010-01-30 | Dayco Europe Srl | PULLEY PACKAGING MACHINE PREFERIBLY TO DRIVE AN ORGAN ACCESSORY VIA A BELT DRIVE IN AN INTERNAL COMBUSTION ENGINE |
| CN102364158A (en) * | 2011-09-07 | 2012-02-29 | 湖北航天化学技术研究所 | Vibration absorber |
| CN104675899A (en) * | 2015-02-13 | 2015-06-03 | 柳州金鸿橡塑有限公司 | Parallel distribution type double-frequency twisting vibration reducer |
| WO2021094557A1 (en) * | 2019-11-15 | 2021-05-20 | Hasse & Wrede Gmbh | Crankshaft arrangement comprising a torsional vibration damper |
| US11761513B2 (en) | 2019-11-15 | 2023-09-19 | Hasse & Wrede Gmbh | Crankshaft arrangement comprising a torsional vibration damper |
| CN114729674B (en) * | 2019-11-15 | 2024-06-25 | 哈瑟&弗雷德有限公司 | Crankshaft assembly with torsional vibration damper |
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|---|---|
| JP3582536B2 (en) | 2004-10-27 |
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