JP2008095787A - Vibration control system - Google Patents

Vibration control system Download PDF

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JP2008095787A
JP2008095787A JP2006277142A JP2006277142A JP2008095787A JP 2008095787 A JP2008095787 A JP 2008095787A JP 2006277142 A JP2006277142 A JP 2006277142A JP 2006277142 A JP2006277142 A JP 2006277142A JP 2008095787 A JP2008095787 A JP 2008095787A
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vibration control
vibration
press
vibration damping
inner peripheral
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Tadayuki Masuda
肇幸 増田
Masashi Kubo
昌史 久保
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Hitachi Ltd
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Hitachi Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration control system in which the tuning width of vibration control is increased, preventing the vibration control device from improvidently moving due to a thermal deterioration of a rubber material. <P>SOLUTION: The vibration control system comprises: a vibration control substrate 11 which is positioned by elastically making a contact with the inner peripheral surface 6a of a drive side tube 6; and a weight 12 for vibration control elastically made contact with the inside of the vibration control substrate 11, and reduces the resonance vibration occurring in the rotation of a propeller shaft. C-shaped urging members 15, 15 made of steel are embedded in press-in portions 13, 13 of the vibration control substrates. Outer peripheries 13b, 13b are urged in the diameter expansion direction by spring force in the diameter expansnion direction of the each urging member, so that outer peripheral surfaces 13c, 13c are always pressed against the inner peripheral surface of the drive side tube. Thereby, the vibration control system is prevented from radially improvidently moving due to the thermal deterioration of the press-in portion. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、例えば車両の変速装置から駆動輪に動力を伝達するプロペラシャフトなどの中空シャフトの内部に取り付けられて、回転中における共振による振動。騒音を低減する制振装置に関する。   The present invention is a vibration caused by resonance during rotation, for example, attached to a hollow shaft such as a propeller shaft that transmits power from a vehicle transmission to drive wheels. The present invention relates to a vibration damping device that reduces noise.

この種の制振装置としては、例えば車両のプロペラシャフトの回転振動・騒音を低減する以下の特許文献１に記載されているものが知られている。   As this type of vibration control device, for example, a device described in Patent Document 1 below that reduces rotational vibration and noise of a propeller shaft of a vehicle is known.

前記車両のプロペラシャフトは、トランスミッション側の中空状の入力軸とデファレンシャルギア側の中空状の出力軸が等速ジョイントや十字継手などの複数の継手によって連結されていると共に、前記入力軸の内部に制振装置が収容保持されている。   In the propeller shaft of the vehicle, a hollow input shaft on the transmission side and a hollow output shaft on the differential gear side are connected by a plurality of joints such as a constant velocity joint and a cruciform joint, and inside the input shaft The damping device is accommodated and held.

この制振装置は、棒状錘と、該棒状錘の両端部をそれぞれ被嵌する分離された２つのゴム部材とを備え、前記各ゴム部材は、剪断特性を有する素材から構成されていると共に、前記棒状錘と同心上に配置されて、それぞれの外端が入力軸チューブの内径よりも大きな外径を有する大径部と、該大径部の内側に一体に形成されて前記棒状錘を被嵌状態に保持する小径な筒状体とから構成されている。   The vibration damping device includes a rod-shaped weight and two separated rubber members that respectively fit both ends of the rod-shaped weight, and each of the rubber members is made of a material having a shearing characteristic, A concentric arrangement with the rod-shaped weight, each of the outer ends having a larger outer diameter than the inner diameter of the input shaft tube, and integrally formed inside the large-diameter portion, covers the rod-shaped weight. It is comprised from the small diameter cylindrical body hold | maintained at a fitting state.

そして、前記プロペラシャフトの入力軸チューブの内部所定位置に前記各ゴム部材を介して圧入保持することにより、前記筒状体と棒状錘を介してプロペラシャフトの回転中に発生する共振振動を低減させて自動車走行時における静粛性を確保するようになっている。   Then, by pressing and holding through the rubber members at predetermined positions inside the input shaft tube of the propeller shaft, the resonance vibration generated during the rotation of the propeller shaft through the cylindrical body and the rod-shaped weight is reduced. This ensures quietness when driving a car.

また、他の従来技術としては、特許文献２に記載されているように、円筒状の制振ゴム材の内部軸方向に棒状体が加硫接着によって固定されていると共に、前記制振ゴム材の外周側には、円筒部材を介して円筒状の弾性部材が一体的に接着固定され、この弾性部材の外周面全体が入力軸チューブの内周面に圧入して入力軸チューブの軸方向の所定位置に固定されるようになっている。   As another prior art, as described in Patent Document 2, a rod-shaped body is fixed by vulcanization adhesion in the internal axial direction of a cylindrical vibration-damping rubber material, and the vibration-damping rubber material A cylindrical elastic member is integrally bonded and fixed to the outer peripheral side of the input member through the cylindrical member. The entire outer peripheral surface of the elastic member is press-fitted into the inner peripheral surface of the input shaft tube, and the axial direction of the input shaft tube is It is fixed in place.

そして、前記制振ゴム材と棒状体によってプロペラシャフトの共振振動を低減させるようになっている。
特開２００２−２９４０２５号公報（図３） 特開平８−８６３３０号公報 And the vibration damping rubber material and the rod-shaped body reduce the resonance vibration of the propeller shaft.
Japanese Patent Laying-Open No. 2002-294025 (FIG. 3) JP-A-8-86330

しかしながら、前者の制振装置にあっては、筒状体を介して制振のチューニングアップは行い易いが、左右２つの大径部の圧接力によって入力軸チューブ内に固定されているため、プロペラシャフトの雰囲気温度の高温化に伴って前記各大径部の外周部が経時的な熱的劣化を起こしやすくなる。このため、入力軸チューブの内周面に対する大径部外周面の圧接力が漸次低下して、制振装置が所定位置から入力軸チューブの内部軸方向へ不用意に移動してしまうおそれがある。   However, in the former vibration damping device, it is easy to tune up the vibration damping through the cylindrical body, but the propeller is fixed in the input shaft tube by the pressure contact force of the two left and right large diameter portions. As the atmospheric temperature of the shaft increases, the outer peripheral portion of each large diameter portion is likely to undergo thermal deterioration over time. For this reason, the pressure contact force of the outer peripheral surface of the large-diameter portion with respect to the inner peripheral surface of the input shaft tube gradually decreases, and the vibration damping device may inadvertently move from the predetermined position toward the internal axis of the input shaft tube. .

この結果、所望の共振振動を低減することができなくなり、移動位置によっては却って共振振動を増幅してしまう可能性がある。   As a result, the desired resonance vibration cannot be reduced, and the resonance vibration may be amplified depending on the moving position.

一方、後者の制振装置にあっては、弾性部材の外周面全体が入力軸チューブの内周面に圧接していることから、強固な圧入状態が得られて熱的劣化による軸方向の不用意な移動は防止できるものの、制振ゴム材が、円筒部材によって弾性部材と分離されていることから、該制振ゴム材のチューニング幅が狭くなってしまい、共振振動を効果的に低減することが困難になる。   On the other hand, in the latter vibration damping device, since the entire outer peripheral surface of the elastic member is in pressure contact with the inner peripheral surface of the input shaft tube, a strong press-fitted state is obtained, and axial instability due to thermal deterioration is obtained. Although the prepared movement can be prevented, since the damping rubber material is separated from the elastic member by the cylindrical member, the tuning width of the damping rubber material is narrowed, and the resonance vibration is effectively reduced. Becomes difficult.

本発明は、ゴム材の熱的劣化による制振装置の不用意な移動を防止しつつ、制振のチューニング幅を大きくすることが可能な制振装置を提供することを目的としている。   An object of the present invention is to provide a vibration damping device capable of increasing the tuning width of vibration damping while preventing inadvertent movement of the vibration damping device due to thermal deterioration of a rubber material.

請求項１に記載の発明は、中空シャフトの内周面に圧接して位置決め保持される制振基体と、該制振基体の内部に弾持された制振用錘と、を備え、前記中空シャフトの回転中に発生する振動を減衰する制振装置であって、前記制振基体を拡径方向へ付勢して前記中空シャフトの内周面に圧接させる付勢部材を設けたことを特徴としている。   The invention according to claim 1 comprises a vibration damping base that is positioned and held in pressure contact with an inner peripheral surface of a hollow shaft, and a vibration damping weight that is held inside the vibration damping base. A damping device that attenuates vibration generated during rotation of the shaft, wherein a biasing member that biases the damping base in a diameter-expanding direction and press-contacts the inner peripheral surface of the hollow shaft is provided. It is said.

この発明によれば、制振基体が付勢部材の拡径方向への付勢力によって、該制振基体の外周面が前記中空シャフトの内周面に常時強く圧接して制振装置が強固に固定されるため、たとえ、制振基体が経時的に熱的劣化しても制振装置を中空シャフトの内部所定位置に確実に保持することが可能になる。   According to the present invention, the damping base is constantly strongly pressed against the inner circumferential face of the hollow shaft by the biasing force of the damping base in the diameter-enlarging direction of the biasing member, so that the damping device is strong. Since it is fixed, the vibration damping device can be reliably held at a predetermined position inside the hollow shaft even if the vibration damping base is thermally deteriorated with time.

この結果、前記制振基体や制振用錘によって常時安定した振動・騒音低減効果が得られる。   As a result, a stable vibration / noise reduction effect can always be obtained by the damping base and the damping weight.

しかも、制振基体の内部に従来のような円筒部材を介在させることがないことから全体のチューニングが容易になる。   In addition, since the conventional cylindrical member is not interposed inside the damping base, the entire tuning becomes easy.

請求項２に記載の発明は、中空シャフトの内周面に圧接して位置決め保持される制振基体と、該制振基体の内部に弾持された制振用錘と、を備え、前記中空シャフトの回転中に発生する振動を減衰する制振装置であって、前記制振基体の外周面に、拡径方向へ弾性変形して前記中空シャフトの内周面に弾接する付勢部材を設けたことを特徴としている。   According to a second aspect of the present invention, there is provided a vibration damping base that is positioned and held in pressure contact with an inner peripheral surface of a hollow shaft, and a vibration damping weight that is held inside the vibration damping base. A vibration damping device that attenuates vibration generated during rotation of a shaft, and is provided with an urging member that elastically deforms in the diameter increasing direction and elastically contacts the inner circumferential surface of the hollow shaft on the outer circumferential surface of the damping base. It is characterized by that.

この発明によれば、付勢部材が自身の弾性ばね力によって常時拡径方向へ広がって、その外周縁が前記中空シャフトの内周面に直接的に圧接することから制振基体がこの付勢部材を介して中空シャフトの内周面に強固に固定される。このため、たとえ、制振基体が経時的に熱的劣化しても制振装置を中空シャフトの内部所定位置に確実に保持することが可能になる。この結果、請求項１の発明と同様な作用効果が得られる。   According to this invention, since the biasing member always expands in the diameter-expanding direction by its own elastic spring force, and the outer peripheral edge thereof is in direct pressure contact with the inner peripheral surface of the hollow shaft, the vibration damping base is thus biased. It is firmly fixed to the inner peripheral surface of the hollow shaft via the member. For this reason, even if the damping base is thermally deteriorated over time, the damping device can be reliably held at a predetermined position inside the hollow shaft. As a result, the same effect as that of the invention of claim 1 can be obtained.

請求項３に記載の発明は、請求項１の発明において、前記付勢部材を、制振基体の内部に一体的に埋設したことを特徴としている。   A third aspect of the invention is characterized in that, in the first aspect of the invention, the urging member is integrally embedded in a damping base.

この発明によれば、請求項１と同様な作用効果が得られることは勿論のこと、制振基体と付勢部材との一体化によって該付勢部材から制振基体に対して拡径方向の付勢力を精度良く伝達できると共に、部品管理が容易になる。   According to the present invention, it is possible to obtain the same function and effect as in the first aspect, but also in the diameter increasing direction from the biasing member to the damping base by integrating the damping base and the biasing member. The urging force can be transmitted with high accuracy and parts management becomes easy.

請求項４に記載の発明は、前記付勢部材を、前記制振基体内部の内周側あるいは外周側に配置したことを特徴としている。   The invention described in claim 4 is characterized in that the urging member is arranged on the inner peripheral side or the outer peripheral side inside the damping base.

以下、本発明にかかる制振装置を車両のプロペラシャフトに適用した実施形態を図面に基づいて詳述する。   Hereinafter, an embodiment in which a vibration damping device according to the present invention is applied to a propeller shaft of a vehicle will be described in detail with reference to the drawings.

前記車両のプロペラシャフト１は、図４に示すように、トランスミッション側に接続された入力軸であるドライブシャフト２と、デファレンシャルギア側に接続された出力軸であるドリブンシャフト３と、ドライブシャフト２とドリブンシャフト３との間に配置された等速ジョイント４及び図外のブラケットを介して車体に支持されたセンターベアリング５とを備えている。   As shown in FIG. 4, the propeller shaft 1 of the vehicle includes a drive shaft 2 that is an input shaft connected to the transmission side, a driven shaft 3 that is an output shaft connected to the differential gear side, and a drive shaft 2. A constant velocity joint 4 disposed between the driven shaft 3 and a center bearing 5 supported by the vehicle body via a bracket (not shown) is provided.

前記ドライブシャフト２は、一端部が前記十字鋼管製の駆動側チューブ６と、該駆動側チューブ６の前端部に溶接などによって軸方向から固定された入力側ヨーク７を介して形成された前端部側の十字継手８などから構成されている。   The drive shaft 2 has a front end portion formed through a drive side tube 6 made of the cross steel pipe and an input side yoke 7 fixed to the front end portion of the drive side tube 6 from the axial direction by welding or the like. It is composed of a side cross joint 8 and the like.

前記ドリブンシャフト２は、図外の鋼管製の従動側チューブと、該従動側チューブの前端部に溶接などによって軸方向から固定されたスタブ軸９などから構成されている。   The driven shaft 2 includes a driven tube made of steel pipe (not shown) and a stub shaft 9 fixed to the front end portion of the driven tube from the axial direction by welding or the like.

また、前記ドライブシャフト２の駆動側チューブ６の内部には、制振装置１０が配置されている。   A vibration damping device 10 is disposed inside the drive side tube 6 of the drive shaft 2.

この制振装置１０は、図１及び図２に示すように、駆動側チューブ６の内周面に弾接して所定位置に位置決め保持される制振基体１１と、該制振基体１１の内部に弾持された制振用錘１２と、を備えている。   As shown in FIGS. 1 and 2, the vibration damping device 10 includes a vibration damping base 11 that is elastically brought into contact with the inner peripheral surface of the driving side tube 6 and positioned and held at a predetermined position. And a damping weight 12 that is supported.

前記制振基体１１は、ゴム材によって一体に形成され、軸方向の両端部に有する大径円環状の一対の圧入部１３、１３と、該各圧入部１３、１３の間の内周側に同心上に一体に形成された円筒状の制振部１４とから構成されている。   The damping base 11 is integrally formed of a rubber material, and a pair of large-diameter annular press-fit portions 13 and 13 at both ends in the axial direction, and an inner peripheral side between the press-fit portions 13 and 13. It is comprised from the cylindrical damping part 14 integrally formed concentrically.

前記両圧入部１３，１３は、内周側の軸心方向に貫通孔１３ａ、１３ａが形成されていると共に、各外周部１３ｂ、１３ｂのそれぞれの両端縁に、圧入部１３，１３の柔軟な弾性力を確保するためにテーパ状の環状切欠部が形成されている。また、平坦な環状の各外周面１３ｃ、１３ｃが、前記駆動側チューブ６の内周面６ａに圧接している。   Both the press-fit portions 13 and 13 are formed with through-holes 13a and 13a in the axial direction on the inner peripheral side, and the press-fit portions 13 and 13 are flexible at both end edges of the outer peripheral portions 13b and 13b. In order to ensure elastic force, a tapered annular notch is formed. Further, the flat annular outer peripheral surfaces 13 c and 13 c are in pressure contact with the inner peripheral surface 6 a of the drive side tube 6.

前記制振部１４は、前記圧入部１３、１３の対向内周側に一体に結合された肉厚な一対の円環部位１４ａ、１４ａと、該両円環部１４ａ、１４ａの対向外周部間に一体に形成された薄肉な円筒部位１４ｂとから構成されている。   The vibration damping portion 14 is formed between a pair of thick annular portions 14a and 14a that are integrally coupled to the opposed inner peripheral sides of the press-fit portions 13 and 13, and the opposed outer peripheral portions of the annular portions 14a and 14a. And a thin cylindrical portion 14b formed integrally with each other.

前記制振用錘１２は、鉄系金属によって一体に形成されて、前記制振部１４の内部に加硫接着によって一体に固着されており、前記制振部１４の円筒部位１４ｂ内に配置されたほぼ円柱状の本体１２ａと、該本体１２ａの両端部に突設され、前記円環部位１４ａ、１４ａの内部に配置された円形状の突起部１２ｂ、１２ｂとから構成されている。   The damping weight 12 is integrally formed of iron-based metal, and is integrally fixed to the inside of the damping part 14 by vulcanization adhesion, and is disposed in the cylindrical portion 14b of the damping part 14. In addition, the main body 12a includes a substantially cylindrical main body 12a and circular protrusions 12b and 12b which are provided at both ends of the main body 12a and are disposed inside the annular portions 14a and 14a.

そして、前記両圧入部１３，１３の内部外周側、つまり前記テーパ状の環状切欠部付近の外周側の内部には、図２にも示すように、ほぼ円環状の一対の付勢部材１５、１５が埋設されている。   And, as shown in FIG. 2, a pair of substantially annular urging members 15, on the inner peripheral side of the press-fitting parts 13, 13, that is, the inner peripheral part in the vicinity of the tapered annular notch, 15 is buried.

この各付勢部材１５，１５は、制振基体１１を型成形などで成形する際に内部に一体に配置され、鋼製金属よって横断面円形状の小径なリング状に形成されていると共に、その円周方向で一部が切り欠かれて全体がＣ字形状に形成されて径方向へ拡がるようなばね力を具有しており、したがって、埋設された各圧入部１３、１３の外周部１３ｂ、１３ｂ側を拡径方向へ付勢するようになっている。   Each of the urging members 15 and 15 is integrally disposed inside when the damping base 11 is molded by molding or the like, and is formed into a small ring shape with a circular cross section by a steel metal, A part thereof is cut out in the circumferential direction, and the whole is formed in a C shape and has a spring force that expands in the radial direction. Therefore, the outer peripheral portion 13b of each of the press-fit portions 13 and 13 embedded therein is provided. , 13b is urged in the diameter increasing direction.

したがって、この実施例によれば、制振基体１１の各圧入部１３，１３の外周部１３ｂ、１３ｂが付勢部材１５、１５によって常時拡径方向へ付勢されて、該各圧入部１３，１３の外周面１３ｃ、１３ｃが前記駆動側チューブ６の内周面６ａに圧接して強固に固定される。このため、たとえ、各圧入部１３，１３が経時的に熱的劣化しても制振装置１を駆動側シャフト６の内部所定位置に確実に保持することが可能になる。   Therefore, according to this embodiment, the outer peripheral portions 13b, 13b of the press-fitting portions 13, 13 of the damping base 11 are always urged in the diameter-expanding direction by the urging members 15, 15, so that the press-fitting portions 13, 13 outer peripheral surfaces 13c, 13c are pressed against the inner peripheral surface 6a of the drive side tube 6 and firmly fixed. For this reason, even if the respective press-fitting portions 13 and 13 are thermally deteriorated with time, the vibration damping device 1 can be reliably held at a predetermined position inside the drive-side shaft 6.

この結果、前記制振基体１１や制振用錘１２によって常時安定した振動・騒音の低減効果が得られる。   As a result, a stable vibration / noise reduction effect can be obtained by the damping base 11 and the damping weight 12 at all times.

しかも、制振基体１１の内部に従来のような円筒部材を介在させることがなく、制振基体１１の圧入部１３、１３と制振部１４とが一体であり、かつ制振用錘１２が円筒部位１４に弾持されていることから、共振に対するチューニングを容易に行うことが可能になる。   In addition, the conventional cylindrical member is not interposed inside the damping base 11, the press-fitting parts 13, 13 of the damping base 11 and the damping part 14 are integrated, and the damping weight 12 is provided. Since it is held by the cylindrical portion 14, tuning for resonance can be easily performed.

また、制振基体１１と付勢部材１５、１５との一体化によって該付勢部材１５，１５の脱落が防止できることは勿論のこと、該付勢部材１５，１５から制振基体１１に対して付勢力を精度良く伝達できると共に、部品管理が容易になる。   In addition, it is possible to prevent the biasing members 15 and 15 from falling off by integrating the vibration damping base 11 and the biasing members 15 and 15, and from the biasing members 15 and 15 to the vibration damping base 11. The urging force can be transmitted with high accuracy and parts management becomes easy.

なお、前記圧入部１３，１３は、円環状に変えて図３に示すようにほぼ十字形状に形成することも可能であり、このようにすれば、圧入部１３，１３の弾性力が柔軟になってチューニングが行い易くなり、より精度の高い振動・騒音の低減効果が得られる。   The press-fitting parts 13 and 13 can be formed in a substantially cross shape as shown in FIG. 3 instead of an annular shape. In this way, the elastic force of the press-fitting parts 13 and 13 is flexible. As a result, tuning is facilitated, and a more accurate vibration / noise reduction effect can be obtained.

図５は本発明の第２の実施例を示し、制振基体１１と付勢部材１５、１５とを別体に形成したもので、各圧入部１３，１３の外側面に円形溝１３ｅ、１３ｅがそれぞれ形成されていると共に、各圧入部１３，１３の外周部１３ｂ、１３ｂ内に前記円形溝１３ｅ、１３ｅに臨む大径な円環状の保持溝１３ｆ、１３ｆがそれぞれ形成されている。一方、付勢部材１５，１５は、前記実施例と同様にほぼＣ字形状の小径な鋼製によって形成されている。   FIG. 5 shows a second embodiment of the present invention, in which the damping base 11 and the urging members 15 and 15 are formed separately, and circular grooves 13e and 13e are formed on the outer surfaces of the press-fit portions 13 and 13, respectively. Are formed, and large-diameter annular holding grooves 13f and 13f facing the circular grooves 13e and 13e are formed in the outer peripheral portions 13b and 13b of the press-fitting portions 13 and 13, respectively. On the other hand, the urging members 15 and 15 are formed of a substantially C-shaped small-diameter steel as in the above embodiment.

したがって、制振基体１１を型成形などによって成形した後に、各付勢部材１５、１５を縮径させながら円形溝１３ｅ、１３ｅに軸方向から嵌入させて保持溝１３ｆ、１３ｆに位置させた状態で縮径状態を解除すると、自身のばね力によって拡径変形しつつ該保持溝１３ｆ、１３ｆの内部に嵌着固定される。また、この付勢部材１５，１５の拡径方向のばね力によって各圧入部１３，１３の外周部１３ｂ、１３ｂが拡径方向へ付勢される。   Accordingly, after the vibration damping base 11 is molded by molding or the like, the biasing members 15 and 15 are reduced in diameter and fitted into the circular grooves 13e and 13e from the axial direction and positioned in the holding grooves 13f and 13f. When the reduced diameter state is canceled, the holding grooves 13f and 13f are fitted and fixed while being enlarged and deformed by their own spring force. Further, the outer peripheral portions 13b, 13b of the press-fit portions 13, 13 are urged in the diameter increasing direction by the spring force in the diameter increasing direction of the urging members 15, 15.

したがって、この実施例によれば、前記第１の実施例と同様な作用効果が得られると共に、制振基体１１と各付勢部材１５，１５を別体に形成することによって、付勢部材１５，１５の数量や形状及び材質、外径などを変えることによって各圧入部１３，１３の駆動側チューブ６に対する支持力（圧接力）を自由に設定することが可能になる。   Therefore, according to this embodiment, the same effect as the first embodiment can be obtained, and the biasing member 15 can be formed by forming the damping base 11 and the biasing members 15 and 15 separately. , 15 by changing the quantity, shape, material, outer diameter, etc., it is possible to freely set the support force (pressure contact force) of the press-fitting portions 13, 13 with respect to the drive side tube 6.

図６は第３の実施例を示し、各圧入部１３の外周面１３ｃ、１３ｃに各付勢部材１５、１５を配置固定したものである。   FIG. 6 shows a third embodiment in which the urging members 15 and 15 are arranged and fixed on the outer peripheral surfaces 13c and 13c of the press-fitting portions 13 respectively.

すなわち、前記各外周面１３ｃ、１３ｃの軸方向のほぼ中央位置に、円環溝１３ｇ、１３ｇが形成されており、この円環溝１３ｇ、１３ｇは、横断面ほぼＵ字形状に形成されて外端が開口されている。一方、付勢部材１５，１５は、前記各実施例と同じくほぼＣ字形状の小径な鋼製によって形成されているが、他の実施例のものよりも大径に形成されて、自身のばね力によって円環溝１３ｇ、１３ｇに嵌着固定されていると共に、外周縁が前記円環溝１３ｇ、１３ｇの開口から僅かに突出して駆動側チューブ６の内周面６ａに拡径方向へ直接的に圧接している。   That is, the annular grooves 13g and 13g are formed at substantially the center position in the axial direction of the outer peripheral surfaces 13c and 13c. The annular grooves 13g and 13g are formed in a substantially U-shaped cross section and are externally formed. The end is open. On the other hand, the urging members 15 and 15 are made of a substantially C-shaped small-diameter steel as in the above-described embodiments, but are formed to have a larger diameter than those of the other embodiments and have their own springs. The outer circumferential edge slightly protrudes from the opening of the annular grooves 13g, 13g and is directly attached to the inner peripheral surface 6a of the drive side tube 6 in the diameter increasing direction. Is in pressure contact.

したがって、この実施例によれば、付勢部材１５，１５が自身の弾性ばね力によって常時拡径方向へ広がって、その外周縁が前記駆動側チューブ６の内周面６ａに直接的に圧接していることから、制振基体１１がこの付勢部材１５，１５を介して駆動側チューブ６の内周面６ａに強固に固定される。   Therefore, according to this embodiment, the urging members 15, 15 always expand in the diameter-expanding direction by their own elastic spring force, and the outer peripheral edge directly presses against the inner peripheral surface 6 a of the drive side tube 6. Therefore, the vibration damping base 11 is firmly fixed to the inner peripheral surface 6a of the drive side tube 6 through the biasing members 15 and 15.

このため、たとえ、制振基体１１が経時的に劣化しても制振装置１を駆動側チューブ６の内部所定位置に確実に保持することが可能になる。この結果、前記各実施例と同様な作用効果が得られる。   For this reason, even if the damping base 11 deteriorates with time, the damping device 1 can be reliably held at a predetermined position inside the drive side tube 6. As a result, the same effects as those of the above embodiments can be obtained.

図７は第４の実施例を示し、制振基体１１の構造を変更したものであって、制振基体１１全体がほぼ円筒状に形成されて、制振部１４は、内部軸方向に均一径の円柱状の支持溝１４ｃが貫通形成され、この支持溝１４ｃに円柱状に形成された制振用錘１２が加硫接着されている。また、圧入部１３の外周面１３ｄの全体が駆動側チューブ６の内周面６ａに圧入固定されている。   FIG. 7 shows a fourth embodiment in which the structure of the damping base 11 is changed. The entire damping base 11 is formed in a substantially cylindrical shape, and the damping portion 14 is uniform in the direction of the internal axis. A cylindrical support groove 14c having a diameter is formed so as to penetrate therethrough, and a damping weight 12 formed in a columnar shape is vulcanized and bonded to the support groove 14c. Further, the entire outer peripheral surface 13 d of the press-fit portion 13 is press-fitted and fixed to the inner peripheral surface 6 a of the drive side tube 6.

一方、付勢部材１５，１５は、構造は前記第１，第２実施例と同様にＣ字形状に形成されて、前記圧入部１３の軸方向の前後端部内に埋設されており、制振基体１１の成形時に内部に一体的に加硫接着されるようになっている。   On the other hand, the urging members 15 and 15 are formed in a C shape similarly to the first and second embodiments, and are embedded in the front and rear end portions of the press-fit portion 13 in the axial direction. When the base 11 is molded, it is integrally vulcanized and bonded inside.

したがって、この実施例も各付勢部材１５，１５の拡径方向のばね力によって圧入部１３の前後端部が拡径方向へ付勢されて、駆動側チューブ６の内周面６ａに常時強固に圧接するため、前記各実施例と同様な作用効果が得られる。   Therefore, also in this embodiment, the front and rear end portions of the press-fitting portion 13 are urged in the diameter increasing direction by the spring force in the diameter increasing direction of the urging members 15, 15, so that the inner peripheral surface 6 a of the drive side tube 6 is always firmly fixed. Therefore, the same effects as those of the above embodiments can be obtained.

本発明は、前記各実施例の構成に限定されるものではなく、例えば第１実施例における付勢部材１５、１５を各圧入部１３、１３のさらに外周側の位置あるいは内周側に埋設することも可能である。また、プロペラシャフト１の仕様や外径によって前記各付勢部材１５の線径や外形などを適宜変更してばね力を大小変化させることも可能である。また、本発明は、前記プロペラシャフト１以外の回転軸部材に適用することも可能である。   The present invention is not limited to the configuration of each of the above-described embodiments. For example, the urging members 15 and 15 in the first embodiment are embedded in the positions on the outer peripheral side or the inner peripheral side of the press-fit portions 13 and 13. It is also possible. Further, the spring force can be changed in magnitude by appropriately changing the wire diameter and outer shape of each urging member 15 according to the specification and outer diameter of the propeller shaft 1. Further, the present invention can also be applied to rotating shaft members other than the propeller shaft 1.

本発明の制振装置をプロペラシャフトに適用した第１実施例の要部縦断面図である。It is a principal part longitudinal cross-sectional view of 1st Example which applied the damping device of this invention to the propeller shaft. 図１のＡ−Ａ線断面図である。It is the sectional view on the AA line of FIG. 制振基体の圧入部の他例を示す図１のＢ矢視図である。FIG. 7 is a view as seen from the direction of the arrow B in FIG. 1 showing another example of the press-fitting portion of the damping base. 本実施例に供されるプロペラシャフトを一部断面して示す側面図である。It is a side view which shows a partial cross section of the propeller shaft used for a present Example. 第２の実施例を示す要部縦断面図である。It is a principal part longitudinal cross-sectional view which shows a 2nd Example. 第３の実施例を示す要部縦断面図である。It is a principal part longitudinal cross-sectional view which shows a 3rd Example. 第４の実施例を示す要部縦断面図である。It is a principal part longitudinal cross-sectional view which shows a 4th Example.

符号の説明Explanation of symbols

１…プロペラシャフト
２…ドライブシャフト
３…ドリブンシャフト
６…駆動側チューブ（中空シャフト）
６ａ…内周面
１０…制振装置
１１…制振基体
１２…制振用錘
１３…圧入部
１４…制振部
１５…付勢部材 DESCRIPTION OF SYMBOLS 1 ... Propeller shaft 2 ... Drive shaft 3 ... Driven shaft 6 ... Drive side tube (hollow shaft)
6a ... Inner peripheral surface 10 ... Damping device 11 ... Damping base 12 ... Damping weight 13 ... Press-fit portion 14 ... Damping portion 15 ... Biasing member

Claims (4)

中空シャフトの内周面に圧接して位置決め保持される制振基体と、該制振基体の内部に弾持された制振用錘と、を備え、前記中空シャフトの回転中に発生する振動を減衰する制振装置であって、
前記制振基体を拡径方向へ付勢して前記中空シャフトの内周面に圧接させる付勢部材を設けたことを特徴とする制振装置。 A vibration damping base that is positioned and held in pressure contact with the inner peripheral surface of the hollow shaft; A damping device for damping,
A vibration damping device comprising a biasing member that biases the vibration damping base in a diameter-expanding direction and press-contacts the inner surface of the hollow shaft. 中空シャフトの内周面に圧接して位置決め保持される制振基体と、該制振基体の内部に弾持された制振用錘と、を備え、前記中空シャフトの回転中に発生する振動を減衰する制振装置であって、
前記制振基体の外周面に、拡径方向へ弾性変形して前記中空シャフトの内周面に圧接する付勢部材を設けたことを特徴とする制振装置。 A vibration damping base that is positioned and held in pressure contact with the inner peripheral surface of the hollow shaft; A damping device for damping,
The vibration damping device according to claim 1, wherein a biasing member that is elastically deformed in a diameter increasing direction and press-contacted to the inner circumferential surface of the hollow shaft is provided on the outer circumferential surface of the vibration damping base. 前記付勢部材を、制振基体の内部に一体的に埋設したことを特徴とする請求項１に記載の制振装置。 2. The vibration damping device according to claim 1, wherein the urging member is integrally embedded in a vibration damping base. 前記付勢部材を、前記制振基体内部の内周側あるいは外周側に配置したことを特徴とする請求項１に記載の制振装置。 2. The vibration damping device according to claim 1, wherein the biasing member is disposed on an inner circumferential side or an outer circumferential side inside the damping base.
JP2006277142A 2006-10-11 2006-10-11 Vibration control system Pending JP2008095787A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103671699A (en) * 2013-12-23 2014-03-26 江苏科技大学 Inbuilt damping device for hollow shaft
JP2018204714A (en) * 2017-06-06 2018-12-27 Nok株式会社 Dynamic damper

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103671699A (en) * 2013-12-23 2014-03-26 江苏科技大学 Inbuilt damping device for hollow shaft
JP2018204714A (en) * 2017-06-06 2018-12-27 Nok株式会社 Dynamic damper

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