JP2001311433A - Flexible coupling - Google Patents
Flexible couplingInfo
- Publication number
- JP2001311433A JP2001311433A JP2000129462A JP2000129462A JP2001311433A JP 2001311433 A JP2001311433 A JP 2001311433A JP 2000129462 A JP2000129462 A JP 2000129462A JP 2000129462 A JP2000129462 A JP 2000129462A JP 2001311433 A JP2001311433 A JP 2001311433A
- Authority
- JP
- Japan
- Prior art keywords
- flange
- connector
- deformation
- shaft side
- connection elements
- 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
Landscapes
- Vibration Dampers (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、回転軸の接続部に
用いられて、駆動側から従動側へ回転力を伝達すると共
にトルク変動や振動の伝達を低減するフレキシブルカッ
プリングに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flexible coupling used in a connection portion of a rotating shaft to transmit a rotational force from a driving side to a driven side and reduce transmission of torque fluctuation and vibration.
【０００２】[0002]
【従来の技術】自動車のプロペラシャフトとトランスミ
ッション側及びデファレンシャル側との軸接続部等に用
いられるフレキシブルカップリングは、基本的には円周
方向所定間隔で複数配置され駆動軸側に設けられる駆動
側接続子と、これら各駆動側接続子間に位置して円周方
向所定間隔で複数配置され従動軸側に設けられる従動側
接続子と、円周方向に互いに隣り合う前記駆動側及び従
動側接続子の間にそれぞれ介在するエラストマからなる
弾性部材とを備え、回転駆動力を前記弾性部材を介して
伝達すると共に、トルク変動や振動の伝達を前記弾性部
材の変形により低減するものである（例えば特開平１０
−１６９６６７号公報参照）。2. Description of the Related Art A plurality of flexible couplings used for connecting shafts between a propeller shaft of an automobile and a transmission side and a differential side are basically arranged at predetermined intervals in a circumferential direction and are provided on a drive shaft side. A connector, a plurality of driven connectors disposed on the driven shaft side and arranged at predetermined intervals in the circumferential direction between the respective driving connectors, and the drive side and the driven side connections circumferentially adjacent to each other; And an elastic member made of an elastomer interposed between the respective members. The elastic member is configured to transmit rotational driving force via the elastic member, and reduce transmission of torque fluctuation and vibration by deformation of the elastic member (for example, JP Hei 10
169667).
【０００３】[0003]
【発明が解決しようとする課題】ところで、この種のフ
レキシブルカップリング（軸継ぎ手）において、有効な
防振・防音効果を実現するには、ばね定数を低くする必
要があり、動力伝達を行うためにはある程度ばね定数を
高く設定する必要があるといった、相反する特性が要求
される。しかしながら、上記従来技術によれば、駆動側
と従動側との相対的な捩り角度に対して、弾性部材が、
ほぼ線形的な荷重特性しか得られない構造であるため、
上記特性を満足することが困難であり、したがって、双
方の特性の妥協点を見出して仕様の設定を行う必要があ
った。By the way, in this type of flexible coupling (shaft coupling), it is necessary to lower the spring constant in order to realize an effective vibration-proof and sound-proof effect. Are required to have contradictory characteristics such as a need to set a certain high spring constant. However, according to the above prior art, the elastic member has a relative torsion angle between the driving side and the driven side.
Because it is a structure that can obtain only an almost linear load characteristic,
It is difficult to satisfy the above characteristics, and therefore, it is necessary to find a compromise between the two characteristics and set the specifications.
【０００４】本発明は、上述のような問題に鑑みてなさ
れたもので、その主な技術的課題とするところは、優れ
た防振・防音性能と、動力伝達力の双方を満足し得るフ
レキシブルカップリングを提供することにある。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and has as its main technical problems a flexible vibration-proofing device capable of satisfying both excellent vibration and sound insulation performance and power transmission force. It is to provide a coupling.
【０００５】[0005]
【課題を解決するための手段】上述した技術的課題を有
効に解決するための手段として、本発明に係るフレキシ
ブルカップリングは、円周方向所定間隔で複数配置され
駆動軸側及び従動軸側のうちの一方に設けられる第一接
続子と、これら各第一接続子間に位置して円周方向所定
間隔で複数配置され駆動軸側及び従動軸側のうちの他方
に設けられる第二接続子と、円周方向に互いに隣り合う
前記第一及び第二接続子の間にそれぞれ介在し前記第一
接続子側に固定されたエラストマからなる弾性部材とを
備え、前記弾性部材は、前記第二接続子側と初期接触す
る第一山部と、この第一山部が所定の変形量に達した時
点で前記第二接続子側と接触する第二山部が形成されて
いる。また、この構成において一層好ましくは、前記弾
性部材に、前記第一山部の変形による応力を吸収する逃
げ溝が、前記第一山部に隣接して形成される。Means for Solving the Problems As means for effectively solving the above-mentioned technical problems, a plurality of flexible couplings according to the present invention are arranged at predetermined intervals in a circumferential direction and are arranged on a drive shaft side and a driven shaft side. A first connector provided on one of the first connectors, and a second connector provided on the other of the drive shaft side and the driven shaft side, which is disposed between the first connectors and at a plurality of circumferentially predetermined intervals. And an elastic member made of an elastomer interposed between the first and second connectors adjacent to each other in the circumferential direction and fixed to the first connector side, wherein the elastic member is A first peak portion that makes initial contact with the connector side and a second peak portion that contacts the second connector side when the first peak portion reaches a predetermined deformation amount are formed. More preferably, in this configuration, a relief groove for absorbing stress due to deformation of the first ridge is formed in the elastic member adjacent to the first ridge.
【０００６】この構成によれば、トルク変動等によっ
て、第一接続子と第二接続子の間で弾性部材が変形を受
ける過程では、この弾性部材は、まず第一山部のみが変
形を受け、特に、この第一山部に隣接する逃げ溝が形成
されることによって、第一山部の変形による応力が吸収
されるのでばね定数が低く、有効な防振・防音効果を奏
する。また、第一及び第二接続子の互いの捩れ角が所定
の大きさになると、第二山部も変形を受けることによっ
て、ばね定数が上昇するので、所要の動力伝達力が確保
される。According to this configuration, in a process in which the elastic member is deformed between the first connector and the second connector due to torque fluctuation or the like, first, only the first peak portion of the elastic member is deformed. In particular, since the relief groove adjacent to the first mountain portion is formed, the stress due to the deformation of the first mountain portion is absorbed, so that the spring constant is low and an effective vibration-proof and sound-proof effect is achieved. In addition, when the mutual twist angle of the first and second connectors becomes a predetermined value, the second ridge portion is also deformed, and the spring constant increases, so that the required power transmission force is secured.
【０００７】[0007]
【発明の実施の形態】図１及び図２は、本発明に係るフ
レキシブルカップリングの好ましい実施の形態を示すも
のである。この図において参照符号１は、ボス部１１
と、その外周から円盤状に展開したフランジ本体１２を
有する第一フランジ、参照符号２は、前記第一フランジ
１に軸方向に対向配置され、ボス部２１と、その外周か
ら円盤状に展開したフランジ本体２２と、その外周に沿
って、前記第一フランジ１側へ突出形成された環状の環
状突縁２３を有する第二フランジである。1 and 2 show a preferred embodiment of a flexible coupling according to the present invention. In this figure, reference numeral 1 denotes a boss 11
And a first flange 2 having a flange main body 12 developed in a disk shape from the outer periphery thereof, and a reference numeral 2 is disposed to face the first flange 1 in the axial direction, and is developed in a disk shape from the boss portion 21 and the outer circumference thereof. This is a second flange having a flange main body 22 and an annular annular protruding edge 23 formed to protrude toward the first flange 1 along the outer periphery thereof.
【０００８】第一フランジ１におけるフランジ本体１２
の内側面には、ボス部１１の内端１１ａの外周面から外
径方向に延びる三本の第一接続子１３が、等位相間隔
（円周方向１２０°間隔）で形成されており、第二フラ
ンジ２におけるフランジ本体２２の内側面には、その外
周に沿って形成された環状突縁２３から内径方向に延び
る三本の第二接続子２４が、前記各第一接続子１３，１
３間に位置して等位相間隔（円周方向１２０°間隔）で
形成されている。The flange body 12 of the first flange 1
On the inner side surface, three first connectors 13 extending in the outer radial direction from the outer peripheral surface of the inner end 11a of the boss portion 11 are formed at equal phase intervals (120 ° intervals in the circumferential direction). On the inner side surface of the flange body 22 in the two flanges 2, three second connectors 24 extending in the radial direction from an annular protruding edge 23 formed along the outer periphery are provided with the first connectors 13 and 1 respectively.
3 and are formed at equal phase intervals (120 ° intervals in the circumferential direction).
【０００９】円周方向に交互に隣り合う各第一接続子１
３と各第二接続子２４の間には、エラストマ(ゴム又は
ゴム状弾性材料)からなる弾性部材３Ａ，３Ｂが交互に
介在されている。この弾性部材３Ａ，３Ｂは、図３及び
図４に示されるように、内環部４１及びそこから円周方
向１２０°間隔で外径方向に延びる三本の嵌合プレート
４２を有する取付金具４に一体的に設けられている。The first connectors 1 which are alternately adjacent in the circumferential direction
Elastic members 3A and 3B made of an elastomer (rubber or rubber-like elastic material) are alternately interposed between 3 and each second connector 24. As shown in FIGS. 3 and 4, the elastic members 3A and 3B are provided with a mounting bracket 4 having an inner ring 41 and three fitting plates 42 extending therefrom in the outer diameter direction at intervals of 120 ° in the circumferential direction. Are provided integrally.
【００１０】詳しくは、取付金具４は、内環部４１が、
第二フランジ２におけるボス部２１の外周に遊嵌可能な
大きさに形成され、嵌合プレート４２の先端が、第二フ
ランジ２における環状突縁２３の内径よりも小径の円周
上にある。前記各嵌合プレート４２は、軸方向に開いた
略コ字形の屈曲形状を呈するものであって、第一フラン
ジ１における各第一接続子１３に嵌着されるようになっ
ており、弾性部材３Ａ，３Ｂは、その成形に際して、そ
れぞれ各嵌合プレート４２の円周方向両側に、焼付け等
により一体的に接合されたものである。すなわち、弾性
部材３Ａ，３Ｂは、その各基部が取付金具４における各
嵌合プレート４２を介して第一フランジ１における第一
接続子１３に固定されている。[0010] More specifically, the mounting bracket 4 has an inner ring portion 41,
The fitting plate 42 is formed in a size that can be loosely fitted to the outer periphery of the boss portion 21 in the second flange 2, and the tip of the fitting plate 42 is on a circumference smaller in diameter than the inner diameter of the annular projection 23 in the second flange 2. Each of the fitting plates 42 has a substantially U-shaped bent shape opened in the axial direction, and is adapted to be fitted to each of the first connectors 13 on the first flange 1, and has an elastic member. 3A and 3B are integrally joined to both sides of each fitting plate 42 in the circumferential direction at the time of molding by baking or the like. That is, the bases of the elastic members 3A and 3B are fixed to the first connector 13 of the first flange 1 via the respective fitting plates 42 of the mounting bracket 4.
【００１１】弾性部材３Ａ，３Ｂは、取付金具４におけ
る嵌合プレート４２の中心線を対称軸として、互いに対
称形状に形成されており、その互いに対向する先端部に
は、それぞれ第一山部３１と、その外周側に位置し、円
周方向高さが前記第一山部３１よりも低い第二山部３２
と、これら第一及び第二山部３１，３２の間に位置する
逃げ溝３３が形成されている。半径方向に対する前記第
二山部３２の幅は、前記第一山部３１よりも大きく、前
記逃げ溝３３は、前記第一山部３１と略同等の容積で形
成されている。The elastic members 3A and 3B are formed symmetrically with respect to the center line of the fitting plate 42 in the mounting bracket 4, and are formed symmetrically with each other. And a second peak 32 located on the outer peripheral side and having a circumferential height lower than the first peak 31.
A relief groove 33 is formed between the first and second peaks 31 and 32. The width of the second peak 32 in the radial direction is larger than that of the first peak 31, and the clearance groove 33 is formed with a volume substantially equal to that of the first peak 31.
【００１２】図３に示される弾性部材３Ａ，３Ｂと取付
金具４との一体成形品において、前記弾性部材３Ａ，３
Ｂは、円周方向に互いに対向する第一山部３１，３１間
の間隔ｐ１が、第二フランジ２における第二接続子２４
の円周方向厚さよりも小さく、また、円周方向に互いに
対向する第二山部３２，３２間の間隔ｐ２が、前記第二
接続子２４の円周方向厚さよりも大きいものとなってい
る。したがって図２に示される組立状態において、前記
第一接続子１３と第二接続子２４が、円周方向等間隔
(６０°間隔)にある無負荷状態では、各弾性部材３Ａ，
３Ｂにおける第一山部３１は、先端が所定の潰し代をも
って第二フランジ２における第二接続子２４の両側面に
接触することにより、適当な予圧縮が与えられており、
一方、第二山部３２は、前記第二接続子２４の両側面と
非接触状態にある。In the integrally molded product of the elastic members 3A, 3B and the mounting bracket 4 shown in FIG.
B indicates that the interval p1 between the first peaks 31 facing each other in the circumferential direction is the second connector 24 in the second flange 2.
Is smaller than the circumferential thickness of the second connector 24, and the interval p2 between the second ridges 32, 32 facing each other in the circumferential direction is larger than the circumferential thickness of the second connector 24. . Therefore, in the assembled state shown in FIG. 2, the first connector 13 and the second connector 24 are
In the no-load state (at 60 ° intervals), each elastic member 3A,
The first peak portion 31 in 3B is given an appropriate pre-compression by the tip contacting both side surfaces of the second connector 24 in the second flange 2 with a predetermined crushing allowance,
On the other hand, the second peak portions 32 are in a non-contact state with both side surfaces of the second connector 24.
【００１３】すなわち第一フランジ１と第二フランジ２
の相対的な捩り角が所定の範囲内にあっては、弾性部材
３Ａ，３Ｂは、第一山部３１のみが第二接続子２４の側
面と接触しており、前記捩り角が所定範囲を超えた時点
で、第二山部３２が第二接続子２４の側面と接触される
ようになっている。That is, the first flange 1 and the second flange 2
When the relative torsion angle is within a predetermined range, only the first peak portion 31 of the elastic members 3A and 3B is in contact with the side surface of the second connector 24, and the torsion angle is within the predetermined range. At that point, the second peak 32 comes into contact with the side surface of the second connector 24.
【００１４】また、弾性部材３Ａ，３Ｂの外周面には、
第二フランジ２における環状突縁２３の内周面と摺動可
能に接触される複数の小突起３４が形成されており、軸
方向一端面には、第一フランジ１の内側面と摺動可能に
接触される複数の小突起３５が形成されており、更に軸
方向他端面には、第二フランジ２の内側面と摺動可能に
接触される複数の小突起３６が形成されている。このた
め、弾性部材３Ａ，３Ｂは、前記第一及び第二フランジ
１，２にベタ当たりすることなく保持され、変形動作が
阻害されないようになっている。Further, on the outer peripheral surfaces of the elastic members 3A and 3B,
A plurality of small projections 34 are formed to be slidably in contact with the inner peripheral surface of the annular protruding edge 23 of the second flange 2. One end surface in the axial direction is slidable with the inner surface of the first flange 1. Are formed on the other end surface in the axial direction, and a plurality of small protrusions 36 are formed on the inner surface of the second flange 2 so as to be slidable. For this reason, the elastic members 3A and 3B are held without contacting the first and second flanges 1 and 2 so that the deformation operation is not hindered.
【００１５】上述の構成を備える本発明のフレキシブル
カップリングは、第一フランジ１が、図示されていない
駆動軸及び従動軸のうち一方の軸端に取り付けられ、第
二フランジ２が、前記駆動軸及び従動軸のうち他方の軸
端に取り付けられる。そして、この取付状態で、駆動軸
と従動軸間でトルク変動を生じると、第一フランジ１と
第二フランジ２との相対的な捩り角が変化することによ
って、第一接続子１３と第二接続子２４との間で弾性部
材３Ａ，３Ｂが円周方向へ交互に圧縮変形を受けなが
ら、駆動軸から従動軸への動力伝達を行う。In the flexible coupling of the present invention having the above-described structure, the first flange 1 is attached to one end of a drive shaft and a driven shaft (not shown), and the second flange 2 is attached to the drive shaft. And the other of the driven shafts. Then, when a torque fluctuation occurs between the drive shaft and the driven shaft in this mounted state, the relative twist angle between the first flange 1 and the second flange 2 changes, so that the first connector 13 and the second connector Power is transmitted from the drive shaft to the driven shaft while the elastic members 3A and 3B are alternately compressed and deformed in the circumferential direction between the connector 24 and the elastic member 3A.
【００１６】詳しくは、図２に示される無負荷状態か
ら、例えば一方の弾性部材３Ａが円周方向へ圧縮変形を
受ける過程を考えると、第一フランジ１と第二フランジ
２の相対的な捩り角が所定角度αの範囲内においては、
この弾性部材３Ａは、小突起３４，３６の摺動を伴いな
がら、第一フランジ１及び取付金具４と共に、第二フラ
ンジ２に対して相対的に捩り変位して、第二接続子２４
の側面と接触している第一山部３１が圧縮変形を受ける
が、第二山部３２は非接触状態にある。しかも第一山部
３１は、前記圧縮に伴って、隣接する逃げ溝３３を埋め
るように逃げ変形するので、圧縮による応力が吸収さ
れ、ばね定数が低く抑えられる。More specifically, considering the process in which one elastic member 3A undergoes compressive deformation in the circumferential direction from the no-load state shown in FIG. 2, for example, the relative torsion between the first flange 1 and the second flange 2 is considered. When the angle is within the range of the predetermined angle α,
The elastic member 3 </ b> A is torsionally displaced with the first flange 1 and the mounting bracket 4 relative to the second flange 2 while sliding the small protrusions 34 and 36, and the second connector 24.
The first peak portion 31 that is in contact with the side surface is subjected to compressive deformation, but the second peak portion 32 is in a non-contact state. In addition, the first ridge 31 deforms so as to fill the adjacent escaping groove 33 with the compression, so that the stress due to the compression is absorbed and the spring constant is suppressed low.
【００１７】また、第一フランジ１と第二フランジ２の
相対的な捩り角が、図２に示される所定角度αを超える
と、弾性部材３Ａは、第一山部３１に加えて第二山部３
２も第二接続子２４の側面と接触して圧縮を受ける。し
かも、この時点では前記第一山部３１が逃げ溝３３を充
満するように押し潰されているため、前記弾性部材３Ａ
は、その半径方向全域が第二接続子２４の側面と接触し
て円周方向の圧縮を受けることになり、ばね定数が高く
なる。When the relative torsion angle between the first flange 1 and the second flange 2 exceeds a predetermined angle α shown in FIG. 2, the elastic member 3A Part 3
2 also contacts the side surface of the second connector 24 and receives compression. In addition, at this point, the first ridge portion 31 is crushed so as to fill the clearance groove 33, so that the elastic member 3A
, The entire area in the radial direction comes into contact with the side surface of the second connector 24 and undergoes compression in the circumferential direction, so that the spring constant increases.
【００１８】図２に示される無負荷状態から、他方の弾
性部材３Ｂが円周方向へ圧縮変形を受ける場合も上述と
同様である。The same applies to the case where the other elastic member 3B undergoes a compressive deformation in the circumferential direction from the no-load state shown in FIG.
【００１９】したがって、図５に本発明のフレキシブル
カップリングのばね特性を示すように、捩り角が所定角
度の範囲内では、低ばね定数であることによって、優れ
た防振・防音機能を奏し、それよりも捩り角が大きくな
る加速時等においては、高ばね定数となることによっ
て、大きな動力伝達力が確保される。Therefore, as shown in FIG. 5, the spring characteristics of the flexible coupling of the present invention show that, when the torsion angle is within a predetermined angle range, the spring coupling has a low spring constant, thereby exhibiting excellent vibration and sound insulation functions. At the time of acceleration or the like in which the torsion angle is larger than that, a high spring constant ensures a large power transmission force.
【００２０】また、上述の構成によれば、取付金具４を
介して第一フランジ１の第一接続子１３に固定された弾
性部材３Ａ，３Ｂは、第二フランジ２における環状突縁
２３の内周面に小突起３４で接触していることによっ
て、半径方向へ低いばね定数で変形可能であり、また、
前記第二フランジ２におけるフランジ本体２２の内側面
に、小突起３６において接触していることによって、軸
方向へも低いばね定数で変形可能である。このため、捩
り方向だけでなく、軸方向や半径方向の振動入力に対し
ても、有効な防振・防音機能を奏することができる。Further, according to the above-described configuration, the elastic members 3A and 3B fixed to the first connector 13 of the first flange 1 via the mounting bracket 4 are provided within the annular protruding edge 23 of the second flange 2. By contacting the peripheral surface with the small projections 34, it can be deformed in the radial direction with a low spring constant.
Since the small protrusion 36 contacts the inner surface of the flange main body 22 of the second flange 2, it can be deformed in the axial direction with a low spring constant. For this reason, an effective vibration-proof / sound-proof function can be achieved not only in the torsional direction but also in the axial and radial vibration inputs.
【００２１】なお、本発明は図示の例に限定されるもの
ではなく、各部の形状や、第一及び第二接続子１３，２
４及びこれに対応する弾性部材３Ａ，３Ｂの数等は、種
々変更可能である。It should be noted that the present invention is not limited to the illustrated example, and the shape of each part, the first and second connectors 13, 2
The number of the elastic members 4 and the corresponding elastic members 3A and 3B can be variously changed.
【００２２】[0022]
【発明の効果】本発明のフレキシブルカップリングによ
ると、ばね定数を低くすることによる有効な防振・防音
効果の実現と、ばね定数を高く設定することによる大き
な動力伝達力の確保といった、相反する特性の要求を満
足することができる。According to the flexible coupling of the present invention, contradictory effects such as realizing an effective vibration-proof and sound-proofing effect by lowering the spring constant and securing a large power transmission force by setting the spring constant higher are obtained. It can satisfy the requirements of characteristics.
【図１】本発明に係るフレキシブルカップリングの好ま
しい一実施形態を、軸心と直交する平面で切断して示す
断面図である。FIG. 1 is a sectional view showing a preferred embodiment of a flexible coupling according to the present invention by cutting along a plane perpendicular to an axis.
【図２】図１におけるII−II線断面図である。FIG. 2 is a sectional view taken along line II-II in FIG.
【図３】本発明に係るフレキシブルカップリングにおけ
る弾性部材と取付金具からなる成形品を軸心と平行な方
向から見た図である。FIG. 3 is a view of a molded product including an elastic member and a fitting in the flexible coupling according to the present invention, as viewed from a direction parallel to an axis.
【図４】図３におけるIV−IV線断面図である。FIG. 4 is a sectional view taken along line IV-IV in FIG. 3;
【図５】本発明に係るフレキシブルカップリングの特性
を示す説明図である。FIG. 5 is an explanatory diagram showing characteristics of the flexible coupling according to the present invention.
１ 第一フランジ １１，２１ ボス部 １２，２２ フランジ本体 １３ 第一接続子 ２ 第二フランジ ２３ 環状突縁 ２４ 第二接続子 ３Ａ，３Ｂ 弾性部材 ３１ 第一山部 ３２ 第二山部 ３３ 逃げ溝 ３４〜３６ 小突起 ４ 取付金具 ４１ 内環部 ４２ 嵌合プレート REFERENCE SIGNS LIST 1 first flange 11, 21 boss portion 12, 22 flange body 13 first connector 2 second flange 23 annular protruding edge 24 second connector 3A, 3B elastic member 31 first peak 32 second peak 33 relief groove 34 to 36 Small projection 4 Mounting bracket 41 Inner ring part 42 Fitting plate
Claims (2)
側及び従動軸側のうちの一方に設けられる第一接続子
（１３）と、 これら各第一接続子（１３）間に位置して円周方向所定
間隔で複数配置され駆動軸側及び従動軸側のうちの他方
に設けられる第二接続子（２４）と、 円周方向に互いに隣り合う前記第一及び第二接続子（１
３，２４）の間にそれぞれ介在し前記第一接続子（１
３）側に固定されたエラストマからなる弾性部材（３
Ａ，３Ｂ）とを備え、 前記弾性部材(３Ａ，３Ｂ)は、 前記第二接続子（２４）側と初期接触する第一山部(３
１)と、 この第一山部(３１)の変形が所定の変形量に達した時点
で前記第二接続子（２４）側と接触する第二山部(３２)
が形成されたことを特徴とするフレキシブルカップリン
グ。A first connector (13) which is arranged at predetermined intervals in a circumferential direction and is provided on one of a drive shaft side and a driven shaft side, and is located between the first connectors (13). A second connector (24) which is arranged at predetermined intervals in the circumferential direction and is provided on the other of the drive shaft side and the driven shaft side, and the first and second connectors (1) adjacent to each other in the circumferential direction.
3, 24) and the first connector (1)
3) An elastic member made of an elastomer fixed to the side (3)
A, 3B), and the elastic member (3A, 3B) has a first peak portion (3) that makes initial contact with the second connector (24) side.
1) and a second crest (32) that comes into contact with the second connector (24) when the deformation of the first crest (31) reaches a predetermined amount of deformation.
A flexible coupling characterized in that a flexible coupling is formed.
１)の変形による応力を吸収する逃げ溝(３３)が、前記
第一山部(３１)に隣接して形成されたことを特徴とする
請求項１に記載のフレキシブルカップリング。2. An elastic member (3A, 3B) is provided with a first peak (3).
The flexible coupling according to claim 1, wherein a relief groove (33) for absorbing stress caused by the deformation of (1) is formed adjacent to the first mountain part (31).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000129462A JP4336923B2 (en) | 2000-04-28 | 2000-04-28 | Flexible coupling |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000129462A JP4336923B2 (en) | 2000-04-28 | 2000-04-28 | Flexible coupling |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001311433A true JP2001311433A (en) | 2001-11-09 |
| JP4336923B2 JP4336923B2 (en) | 2009-09-30 |
Family
ID=18638735
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000129462A Expired - Fee Related JP4336923B2 (en) | 2000-04-28 | 2000-04-28 | Flexible coupling |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4336923B2 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003074586A (en) * | 2001-08-30 | 2003-03-12 | Nok Corp | Power transmission device |
| GB2437093A (en) * | 2006-01-05 | 2007-10-17 | Metaldyne Internat France Sas | A torsional isolation device for isolating torque fluctuations in a drive shaft |
| JP2008304068A (en) * | 2008-09-18 | 2008-12-18 | Shinko Electric Co Ltd | Vibration isolating joint |
| KR101071953B1 (en) | 2003-05-08 | 2011-10-11 | 아메리칸 액슬 앤드 매뉴팩쳐링, 인코포레이티드 | Universal joint with torsionally compliant spider assembly |
| KR101271024B1 (en) | 2011-09-27 | 2013-06-04 | 손정남 | Flexible coupling shock absorber |
| JP2014141120A (en) * | 2013-01-22 | 2014-08-07 | Yamaha Motor Co Ltd | Propeller unit and shock absorbing member for the same |
| JP2015169324A (en) * | 2014-03-11 | 2015-09-28 | Nok株式会社 | power transmission coupling |
| EP2960536A4 (en) * | 2013-02-22 | 2016-11-09 | Nabeya Bi Tech Kabushiki Kaisha | Coupling |
| JP7496713B2 (en) | 2020-05-19 | 2024-06-07 | Nok株式会社 | Rotational force transmission mechanism |
-
2000
- 2000-04-28 JP JP2000129462A patent/JP4336923B2/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003074586A (en) * | 2001-08-30 | 2003-03-12 | Nok Corp | Power transmission device |
| KR101071953B1 (en) | 2003-05-08 | 2011-10-11 | 아메리칸 액슬 앤드 매뉴팩쳐링, 인코포레이티드 | Universal joint with torsionally compliant spider assembly |
| GB2437093A (en) * | 2006-01-05 | 2007-10-17 | Metaldyne Internat France Sas | A torsional isolation device for isolating torque fluctuations in a drive shaft |
| JP2008304068A (en) * | 2008-09-18 | 2008-12-18 | Shinko Electric Co Ltd | Vibration isolating joint |
| KR101271024B1 (en) | 2011-09-27 | 2013-06-04 | 손정남 | Flexible coupling shock absorber |
| JP2014141120A (en) * | 2013-01-22 | 2014-08-07 | Yamaha Motor Co Ltd | Propeller unit and shock absorbing member for the same |
| US9840314B2 (en) | 2013-01-22 | 2017-12-12 | Yamaha Hatsudoki Kabushiki Kaisha | Shock absorber for propeller unit, propeller unit, and vessel propulsion apparatus |
| EP2960536A4 (en) * | 2013-02-22 | 2016-11-09 | Nabeya Bi Tech Kabushiki Kaisha | Coupling |
| JP2015169324A (en) * | 2014-03-11 | 2015-09-28 | Nok株式会社 | power transmission coupling |
| JP7496713B2 (en) | 2020-05-19 | 2024-06-07 | Nok株式会社 | Rotational force transmission mechanism |
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| Publication number | Publication date |
|---|---|
| JP4336923B2 (en) | 2009-09-30 |
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