JP2009150431A

JP2009150431A - Torsional vibration reducing device

Info

Publication number: JP2009150431A
Application number: JP2007326723A
Authority: JP
Inventors: Satoshi Kono; 訓河野
Original assignee: Valeo Unisia Transmission KK
Current assignee: Valeo Kapec Japan KK
Priority date: 2007-12-19
Filing date: 2007-12-19
Publication date: 2009-07-09
Anticipated expiration: 2027-12-19
Also published as: JP5060269B2

Abstract

<P>PROBLEM TO BE SOLVED: To increase torsional rigidity of a torsional vibration reducing device including a long travel damper. <P>SOLUTION: This device is provided with a pair of side plates 1, 2 as an input side rotary members, a center plate 3 as an output side rotary member, a pair of springs 5, 6 disposed in series along a circumferential direction between a plurality of first spring seats 7 formed on a pair of the side plates 1, 2 and between second spring seats 3a formed on the center plate 3, and an intermediate member 8 including intermediate spring seats 8b put between a pair of the side plates 1, 2 and between a pair of the springs 5, 6 and an annular part 8a disposed radial direction outside of the second spring seats 3a. First abutment parts 8c are formed at circumferential direction both sides of a base end part of the intermediate spring seat 8b. Second abutment parts 3c abutting on the first abutment parts 8c to interrupt compression of one of a pair of the springs 5, 6 are formed at both side of a tip part of the second spring seat 3a of the center plate 3. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、捩り振動低減装置に関し、捩り量が小さい状態と大きい状態とで、ばね定数が２段階に切り換わるようにしたものである。 The present invention relates to a device for reducing torsional vibration, wherein the spring constant is switched between two levels depending on whether the amount of torsion is small or large.

車両に搭載したエンジンのクランク軸とトランスミッションの入力軸との間には、捩り振動低減装置が設けられている。該捩り振動低減装置は、エンジンのクランク軸に連結される入力側回転部材と、トランスミッションの入力軸に連結される出力側回転部材と、円周方向に沿って配置され前記入力側回転部材と前記出力側回転部材とを円周方向に弾性的に連結するばねとにより構成されている。そして、円周方向に沿って配置されたばねが圧縮されて捩りを生じる際の捩り角度を大きくして捩り剛性を小さくするため、一対のばねを直列に繋いでばねの部分を長くしたロングトラベルダンパ（ＬＴＤダンパ）が設けられる。該ＬＴＤダンパの一対のばねを円弧に近い状態で配置するには、連結する一対のばねの中心線どうしを屈曲させる必要があり、屈曲させると付き合わせた一対のばねの端部の外側には略三角形の隙間が生じる。この隙間を埋めるため、略三角形の中間ばね受部を設け、該中間ばね受部をリング状の環状部を介して連結した中間部材が設けられる。 A torsional vibration reduction device is provided between a crankshaft of an engine mounted on a vehicle and an input shaft of a transmission. The torsional vibration reduction device includes an input-side rotating member coupled to an engine crankshaft, an output-side rotating member coupled to an input shaft of a transmission, the input-side rotating member disposed along a circumferential direction, A spring that elastically connects the output-side rotating member in the circumferential direction. A long travel damper in which a spring portion is elongated by connecting a pair of springs in series in order to reduce the torsional rigidity by increasing the torsion angle when the springs arranged along the circumferential direction are compressed to cause torsion. (LTD damper) is provided. In order to arrange the pair of springs of the LTD damper in a state close to a circular arc, it is necessary to bend the center lines of the pair of springs to be connected. A substantially triangular gap is formed. In order to fill this gap, a substantially triangular intermediate spring receiving portion is provided, and an intermediate member is provided in which the intermediate spring receiving portion is connected via a ring-shaped annular portion.

一対のばねを直列に繋いで中間部材を設けることにより捩り剛性を低減させた従来の捩り振動低減装置として、特許文献１に記載のものが知られている。
特公平５−７７８９１号公報 As a conventional torsional vibration reducing device in which torsional rigidity is reduced by connecting a pair of springs in series and providing an intermediate member, a device disclosed in Patent Document 1 is known.
Japanese Patent Publication No. 5-77891

ところが、近年のエンジンの大容量化，高出力化に伴ってエンジントルクが増大していることに対応して捩り振動低減装置の捩り剛性を増大させ、捩り振動低減効果を維持させる必要が生じており、従来の捩り振動低減装置では捩り剛性が小さく、その特性が常に一定であるため、捩り剛性を増大させることができない。 However, it has become necessary to increase the torsional rigidity of the torsional vibration reducing device and maintain the torsional vibration reducing effect in response to the increase in engine torque with the recent increase in capacity and output of the engine. In the conventional torsional vibration reducing device, the torsional rigidity is small and the characteristics are always constant, so that the torsional rigidity cannot be increased.

そこで本発明は、上記の課題を解決した捩り振動低減装置を提供することを目的とする。 Therefore, an object of the present invention is to provide a torsional vibration reduction device that solves the above-described problems.

請求項１に係る発明は、一対のサイドプレートと該一対のサイドプレートの間に相対回転可能に収容されたセンタープレートとのいずれか一方により構成され駆動源からの入力により回転する入力側回転部材と、他方により構成された出力側回転部材と、前記一対のサイドプレートの夫々の同じ位置に円周方向に沿ってスリットを形成することにより該スリット間に形成された複数の第１ばね受部と、該第１ばね受部と円周方向の同じ位置を占めると共に前記センタープレートから半径方向外側へ向かって突出する第２ばね受部と、前記第１ばね受部間であってかつ前記第２ばね受部間に円周方向に沿って直列配置された一対の弾性部材と、前記一対のサイドプレートの間であってかつ前記第２ばね受部の半径方向外側に配置された環状部と該環状部から半径方向内側へ向かって前記第２ばね受部間へ突出して前記一対の弾性部材の間に介在する中間ばね受部とを有する中間部材とを備えた捩り振動低減装置において、前記中間ばね受部の基端部の円周方向両側に第１当接部を形成する一方、前記入力側回転部材の前記第１ばね受部または前記出力側回転部材の前記第２ばね受部には前記第１当接部に当接して前記一対の弾性部材の一方の圧縮を中断させる第２当接部を形成したことを特徴とする。 The invention according to claim 1 is an input-side rotating member that is configured by any one of a pair of side plates and a center plate that is accommodated between the pair of side plates so as to be relatively rotatable. A plurality of first spring receiving portions formed between the slits by forming a slit along the circumferential direction at the same position of each of the output side rotating member constituted by the other and the pair of side plates. A second spring receiving portion that occupies the same circumferential position as the first spring receiving portion and projects radially outward from the center plate, and between the first spring receiving portion and the first spring receiving portion. A pair of elastic members arranged in series along the circumferential direction between the two spring receiving parts; and an annular part arranged between the pair of side plates and radially outward of the second spring receiving part; In the torsional vibration reduction device, comprising an intermediate member having an intermediate spring receiving portion that protrudes between the second spring receiving portions from the annular portion inward in the radial direction and is interposed between the pair of elastic members. The first contact portion is formed on both sides in the circumferential direction of the base end portion of the spring receiving portion, while the first spring receiving portion of the input side rotating member or the second spring receiving portion of the output side rotating member is A second abutting portion that abuts on the first abutting portion and interrupts compression of one of the pair of elastic members is formed.

この発明によれば、一対のサイドプレートの夫々に形成された第１ばね受部と、センタープレートに形成された第２ばね受部とが相対的に回転することにより、第２当接部が第１当接部に当接するまでの「捩り角度が小さい範囲」では、一対の弾性部材の双方が圧縮され、第２当接部が第１当接部に当接した後の「捩り角度が大きい範囲」では、一方の弾性部材に圧縮力が作用しなくなるので、他方の弾性部材のみが圧縮される。つまり、「捩り角度が小さい範囲」と「捩り角度が大きい範囲」とでは、弾性部材の変位量は略２：１となるため、ばね定数は略１：２となる。ばね定数が２段階に切り換わり、「捩り角度が大きい範囲」では、一対の弾性部材の双方が普通に圧縮される従来の捩り振動低減装置に対し、ばね定数が略２倍に大きくなるので、エンジンの過大トルクを吸収することが可能になる。 According to the present invention, the first spring receiving portion formed on each of the pair of side plates and the second spring receiving portion formed on the center plate relatively rotate, so that the second contact portion is In the “range where the torsion angle is small” until contact with the first contact portion, both of the pair of elastic members are compressed, and the “torsion angle after the second contact portion contacts the first contact portion. In the “large range”, since the compressive force does not act on one elastic member, only the other elastic member is compressed. That is, in the “range where the torsion angle is small” and the “range where the torsion angle is large”, the amount of displacement of the elastic member is about 2: 1, so the spring constant is about 1: 2. The spring constant is switched in two stages, and in the “range where the torsion angle is large”, the spring constant becomes approximately twice as large as that of the conventional torsional vibration reducing device in which both of the pair of elastic members are normally compressed. It becomes possible to absorb the excessive torque of the engine.

請求項２に係る発明は、請求項１に記載の捩り振動低減装置において、前記第１当接部は前記中間ばね受部の基端部の円周方向両側から円周方向へ突出して形成される一方、前記第２当接部は前記センタープレートにおける前記第２ばね受部の半径方向外側であって円周方向両側に円周方向へ突出して形成されていることを特徴とする。 According to a second aspect of the present invention, in the torsional vibration reduction device according to the first aspect, the first abutting portion is formed to protrude in the circumferential direction from both sides in the circumferential direction of the proximal end portion of the intermediate spring receiving portion. On the other hand, the second contact portion is formed to protrude in the circumferential direction on both sides in the circumferential direction on the radially outer side of the second spring receiving portion in the center plate.

この発明によれば、中間ばね受部が形成された中間部材と、センタープレートとは軸方向での同じ位置を占めており、半径方向の外側と内側とに配置されているので、第１当接部と第２当接部との形成が容易である。 According to this invention, the intermediate member on which the intermediate spring receiving portion is formed and the center plate occupy the same position in the axial direction, and are disposed on the outer side and the inner side in the radial direction. It is easy to form the contact portion and the second contact portion.

請求項３に係る発明は、請求項１または２に記載の捩り振動低減装置において、前記一対のサイドプレートどうしを軸方向に連結して結合する連結ピンが設けられ、該連結ピンの半径方向の位置は、前記中間部材の前記環状部と前記センタープレートの前記第２ばね受部との間であることを特徴とする。 According to a third aspect of the present invention, in the torsional vibration reduction device according to the first or second aspect of the present invention, a connection pin that connects the pair of side plates by connecting them in the axial direction is provided, and a radial direction of the connection pin is provided. The position is between the annular portion of the intermediate member and the second spring receiving portion of the center plate.

この発明によれば、連結ピンは半径方向でのセンタープレートの第２ばね受部の外側であって中間部材の環状部の内側に配置されているので、連結ピンがセンタープレートや中間部材に接触することはない。また、連結ピンは円周方向での中間ばね受部どうしの間に配置されているので、連結ピンが中間ばね受部に接触することもない。 According to this invention, since the connecting pin is arranged outside the second spring receiving portion of the center plate in the radial direction and inside the annular portion of the intermediate member, the connecting pin contacts the center plate and the intermediate member. Never do. Further, since the connecting pin is disposed between the intermediate spring receiving portions in the circumferential direction, the connecting pin does not contact the intermediate spring receiving portion.

請求項１に係る捩り振動低減装置によれば、第２当接部が第１当接部に当接するまでの「捩り角度が小さい範囲」では、一対の弾性部材の双方が圧縮され、第２当接部が第１当接部に当接した後の「捩り角度が大きい範囲」では、一方の弾性部材に圧縮力が作用しなくなるので、他方の弾性部材のみが圧縮される。つまり、「捩り角度が小さい範囲」と「捩り角度が大きい範囲」とでは、弾性部材の変位量は略２：１となるため、ばね定数は略１：２となる。ばね定数が２段階に切り換わり、「捩り角度が大きい範囲」では、一対の弾性部材の双方が普通に圧縮される従来の捩り振動低減装置に対し、ばね定数が略２倍に大きくなるので、エンジンの過大トルクを吸収することが可能になる。 According to the torsional vibration reducing device of the first aspect, in the “range where the torsion angle is small” until the second contact portion contacts the first contact portion, both of the pair of elastic members are compressed, and the second In the “range where the torsion angle is large” after the contact portion contacts the first contact portion, the compressive force does not act on one elastic member, so only the other elastic member is compressed. That is, in the “range where the torsion angle is small” and the “range where the torsion angle is large”, the amount of displacement of the elastic member is about 2: 1, so the spring constant is about 1: 2. The spring constant is switched in two stages, and in the “range where the torsion angle is large”, the spring constant becomes approximately twice as large as that of the conventional torsional vibration reducing device in which both of the pair of elastic members are normally compressed. It becomes possible to absorb the excessive torque of the engine.

請求項２に係る捩り振動低減装置によれば、中間ばね受部が形成された中間部材と、センタープレートとは軸方向での同じ位置であって、半径方向の外側と内側とに配置されているので、第１当接部と第２当接部との形成が容易である。 According to the torsional vibration reducing device of the second aspect, the intermediate member in which the intermediate spring receiving portion is formed and the center plate are disposed at the same position in the axial direction, and are disposed on the outer side and the inner side in the radial direction. Therefore, it is easy to form the first contact portion and the second contact portion.

請求項３に係る捩り振動低減装置によれば、連結ピンは半径方向でのセンタープレートの第２ばね受部の外側であって中間部材の環状部の内側に配置されているので、連結ピンがセンタープレートや中間部材に接触することはない。また、連結ピンは円周方向での中間ばね受部どうしの間に配置されているので、連結ピンが中間ばね受部に接触することもない。 According to the torsional vibration reducing device of the third aspect, the connecting pin is disposed outside the second spring receiving portion of the center plate in the radial direction and inside the annular portion of the intermediate member. There is no contact with the center plate or intermediate member. Further, since the connecting pin is disposed between the intermediate spring receiving portions in the circumferential direction, the connecting pin does not contact the intermediate spring receiving portion.

以下、本発明による捩り振動低減装置の実施の形態を説明する。 Embodiments of a torsional vibration reducing device according to the present invention will be described below.

駆動源であるエンジンからの入力により回転する入力側回転部材として一対のサイドプレート１，２が設けられている。該一対のサイドプレート１，２は、板状材を円板形に成形したものである。一対のサイドプレート１，２の間には相対回転可能にセンタープレート３が収容され、出力側回転部材を構成している。 A pair of side plates 1 and 2 is provided as an input side rotating member that rotates by an input from an engine that is a drive source. The pair of side plates 1 and 2 are formed by forming a plate-like material into a disk shape. A center plate 3 is accommodated between the pair of side plates 1 and 2 so as to be relatively rotatable, and constitutes an output side rotating member.

一対のサイドプレート１，２とセンタープレート３との間には、弾性部材としてのばね４とばね５とが配置されている。これらの一対のばね４，５を収容する部分の構成について説明する。一対のサイドプレート１，２には、円周方向および半径方向の同じ位置に、円周方向に沿って略等間隔に３つのスリット６が形成されている。これにより、円周方向におけるスリット６どうしの間には第１ばね受部７が形成されている。一方、一対のサイドプレート１，２の第１ばね受部７と対応する位置には、センタープレート３から半径方向外側へ突出する第２ばね受部３ａが形成されている。第１ばね受部７間であってかつ前記第２ばね受部３ａ間の位置、即ちスリット６の位置に、円周方向に沿って弾性部材としての一対のばね４，５が設けられている。一対のばね４，５は、夫々ばね定数の大きいものとばね定数の小さいものとが組み合わせて設けられている。即ち、ばね４は外径寸法の大きい親ばね４ａと外径寸法の小さい子ばね４ｂとにより構成され、ばね５は外径寸法の大きい親ばね５ａと外径寸法の小さい子ばね５ｂとにより構成されている。 Between the pair of side plates 1 and 2 and the center plate 3, a spring 4 and a spring 5 are disposed as elastic members. The structure of the part which accommodates these pair of springs 4 and 5 is demonstrated. In the pair of side plates 1 and 2, three slits 6 are formed at substantially equal intervals along the circumferential direction at the same position in the circumferential direction and the radial direction. Thereby, the 1st spring receiving part 7 is formed between the slits 6 in the circumferential direction. On the other hand, a second spring receiving portion 3 a that protrudes radially outward from the center plate 3 is formed at a position corresponding to the first spring receiving portion 7 of the pair of side plates 1 and 2. A pair of springs 4, 5 as elastic members are provided along the circumferential direction between the first spring receiving portions 7 and between the second spring receiving portions 3 a, that is, at the positions of the slits 6. . The pair of springs 4 and 5 is provided in combination with a spring having a large spring constant and a spring having a small spring constant. That is, the spring 4 is constituted by a parent spring 4a having a large outer diameter and a child spring 4b having a small outer diameter, and the spring 5 is constituted by a parent spring 5a having a large outer diameter and a child spring 5b having a small outer diameter. Has been.

前記一対のサイドプレート１，２の間であってセンタープレート３の半径方向外側には、中間部材としてのフローティングイコライザ８が収容されている。該フローティングイコライザ８は、環状部８ａと該環状部８ａから半径方向内側へ向かって突出する３つの略三角形状の中間ばね受部８ｂとにより構成されている。そして、中間ばね受部８ｂの部分が、前記一対のばね４，５の間に介在し、ばね４，５の端部を受けている。 A floating equalizer 8 serving as an intermediate member is accommodated between the pair of side plates 1 and 2 and outside the center plate 3 in the radial direction. The floating equalizer 8 includes an annular portion 8a and three substantially triangular intermediate spring receiving portions 8b that protrude radially inward from the annular portion 8a. A portion of the intermediate spring receiving portion 8 b is interposed between the pair of springs 4 and 5 and receives the end portions of the springs 4 and 5.

出力側回転部材としての前記センタープレート３を図示しないトランスミッションの入力軸に連結するため、該センタープレート３の軸心位置には筒部３ｂが一体形成されている。該筒部３ｂの内周面には内歯３ｄが形成され、該内歯３ｄが図示しないトランスミッションの入力軸の外周面に形成された外歯と係合する。 In order to connect the center plate 3 as the output side rotation member to an input shaft of a transmission (not shown), a cylindrical portion 3 b is integrally formed at the axial center position of the center plate 3. Inner teeth 3d are formed on the inner peripheral surface of the cylindrical portion 3b, and the inner teeth 3d engage with outer teeth formed on the outer peripheral surface of the transmission input shaft (not shown).

一方、入力側回転部材としての一対のサイドプレート１，２のうちの一方のサイドプレート１は、エンジンのクランク軸に連結されている。即ち、図１（ａ）における左方に位置するエンジンのクランク軸にフライホィールマス９が設けられており、該フライホィールマス９に摩擦板１０が取り付けられる一方、フリーな状態のプレッシャプレート１１にはリング状の摩擦板１２が結合され、該摩擦板１２には図１（ｂ）に示すように略四角形の薄板である連結部材１３が２つのリベット１４を介して複数枚結合され、該連結部材１３から内側へ突出する突出部の夫々には、前記サイドプレート１の外周部が３つのリベット１５を介して結合されている。このように一体に結合されてフリーなプレッシャプレート１１と摩擦板１２と連結部材１３とが、板ばね１６の付勢力により常時摩擦板１０へ向かって付勢されている。このため、一対のサイドプレート１，２はエンジンのクランク軸と一体になって回転する。なお、摩擦板１０には、フライホィールマス９の内部と外部とを連通させる油孔１０ａが形成されている。 On the other hand, one side plate 1 of the pair of side plates 1 and 2 as the input side rotating member is connected to an engine crankshaft. That is, a flywheel mass 9 is provided on the crankshaft of the engine located on the left side in FIG. 1A, and a friction plate 10 is attached to the flywheel mass 9, while the pressure plate 11 is free. A ring-shaped friction plate 12 is coupled, and a plurality of coupling members 13, which are substantially rectangular thin plates, are coupled to the friction plate 12 via two rivets 14 as shown in FIG. Each of the protruding portions protruding inward from the member 13 is connected to the outer peripheral portion of the side plate 1 via three rivets 15. The pressure plate 11, the friction plate 12, and the connecting member 13 that are integrally coupled in this way are constantly urged toward the friction plate 10 by the urging force of the leaf spring 16. For this reason, the pair of side plates 1 and 2 rotate integrally with the crankshaft of the engine. The friction plate 10 is formed with an oil hole 10a that allows the inside and outside of the flywheel mass 9 to communicate with each other.

一対のばね４，５が円周方向へ一定量だけ圧縮されたら、それ以上は一方のみが圧縮されないようにするため、前記三角形の中間ばね受部８ｂの基端部の円周方向両側から円周方向へ突出させて第１当接部８ｃが形成される一方、該第１当接部８ｃに当接して一対のばね４，５の一方の圧縮を中断させる第２当接部３ｃがセンタープレート３の第２ばね受部３ａに形成されている。即ち、第２当接部３ｃが、センタープレート３における第２ばね受部３ａの半径方向外側であって円周方向両側に、円周方向へ突出して形成されている。 When the pair of springs 4 and 5 are compressed by a certain amount in the circumferential direction, only one of the springs 4 and 5 is compressed from the both sides in the circumferential direction of the base end of the triangular intermediate spring receiving portion 8b. The first contact portion 8c is formed by protruding in the circumferential direction, and the second contact portion 3c that contacts the first contact portion 8c and interrupts compression of one of the pair of springs 4 and 5 is the center. A second spring receiving portion 3 a of the plate 3 is formed. That is, the second contact portion 3c is formed to protrude in the circumferential direction on the radially outer side of the second spring receiving portion 3a in the center plate 3 and on both sides in the circumferential direction.

一対のサイドプレート１，２どうしを軸方向に連結して結合する連結ピン１７が設けられている。該連結ピン１７の半径方向および円周方向の位置は、前記中間部材８の前記環状部８ａと前記センタープレー３の第２ばね受部３ａとの間に配置されている。即ち、一対のサイドプレート１，２の夫々の第１ばね受部７の基端部の中央には四角形の結合孔が形成され、該結合孔に連結ピン１７が挿通され、該連結ピン１７の両端部には、抜け止め用のかしめが行われている。 A connecting pin 17 is provided for connecting and connecting the pair of side plates 1 and 2 in the axial direction. The positions of the connecting pin 17 in the radial direction and the circumferential direction are arranged between the annular portion 8 a of the intermediate member 8 and the second spring receiving portion 3 a of the center play 3. That is, a square coupling hole is formed in the center of the base end portion of the first spring receiving portion 7 of each of the pair of side plates 1 and 2, and the coupling pin 17 is inserted into the coupling hole. The both ends are caulked for retaining.

次に、作用を説明する。 Next, the operation will be described.

この発明によれば、一対のサイドプレート１，２の夫々に形成された第１ばね受部７と、センタープレート３に形成された第２ばね受部３ａとが相対的に回転することにより、第２当接部３ｃが第１当接部８ｃに当接するまでの「捩り角度が小さい範囲」では一対のばね４，５の双方が同時に圧縮され、第２当接部３ｃが第１当接部８ｃに当接してからの「捩り角度が大きい範囲」では一対のばね４，ばね５のいずれか一方に圧縮力が作用しなくなるので、他方のみが圧縮される。つまり、「捩り角度が小さい範囲」ではねじりばね定数が小さくエンジンからのトルク変動入力を十分に減衰させることができる一方、「捩り角度が大きい範囲」ではねじりばね定数が大きく過大なトルクを吸収できる。「捩り角度が小さい範囲」と「捩り角度が大きい範囲」とでは、一対のばね４，５の全体の変位量は略２：１となるため、ばね定数は略１：２となり、「捩り角度が大きい範囲」では、一対のばね４，５の双方が普通に圧縮される従来の捩り振動低減装置に対し、ばね定数が略２倍に大きくなるので、エンジンの過大トルクを吸収することが可能になる。 According to this invention, when the 1st spring receiving part 7 formed in each of a pair of side plates 1 and 2 and the 2nd spring receiving part 3a formed in the center plate 3 rotate relatively, In the “range where the torsion angle is small” until the second contact portion 3c contacts the first contact portion 8c, both the pair of springs 4 and 5 are compressed at the same time, and the second contact portion 3c becomes the first contact. In the “range where the torsion angle is large” after coming into contact with the portion 8 c, the compression force does not act on either one of the pair of springs 4 and 5, so only the other is compressed. In other words, in the “range where the torsion angle is small”, the torsion spring constant is small and the torque fluctuation input from the engine can be sufficiently attenuated, while in the “range where the torsion angle is large”, the torsion spring constant is large and excessive torque can be absorbed. . In the “range where the torsion angle is small” and “range where the torsion angle is large”, the total displacement amount of the pair of springs 4 and 5 is about 2: 1, so the spring constant is about 1: 2. In the "large range", the spring constant is almost twice as large as that of the conventional torsional vibration reducing device in which both of the pair of springs 4 and 5 are normally compressed, so it is possible to absorb the excessive torque of the engine. become.

図２は捩り振動低減装置の捩り角度、即ち一対のサイドプレート１，２とセンタープレー３とのなす角度と、一対のばね４，５によるトルクとの関係を示すグラフである。第２当接部３ｃが第１当接部８ｃに当接するときの捩り角度αの時点でのトルクをＴ１とし、当接してから捩り角度がβになった時点でのトルクをＴｍａｘとすると、捩り角度がαまでの「捩り角度が小さい範囲」では一対のばね４，５の双方が同時に圧縮されるので傾きが小さくねじりばね定数が小さい。一方、捩り角度がαからβまでの「捩り角度が大きい範囲」では一対のばね４，５の一方のみが圧縮されるので傾きが大きくねじりばね定数が大きくなる。 FIG. 2 is a graph showing the relationship between the torsional angle of the torsional vibration reducing device, that is, the angle between the pair of side plates 1 and 2 and the center play 3 and the torque by the pair of springs 4 and 5. When the torque at the time of the twist angle α when the second contact portion 3c contacts the first contact portion 8c is T1, and the torque when the twist angle becomes β after the contact is Tmax, In the “range where the torsion angle is small” up to the torsion angle α, both the pair of springs 4 and 5 are compressed simultaneously, so the inclination is small and the torsion spring constant is small. On the other hand, in the “range where the torsion angle is large” from α to β, only one of the pair of springs 4 and 5 is compressed, so the inclination is large and the torsion spring constant is large.

捩り振動低減装置では、エンジンの最大トルクまでは十分な捩り振動減衰効果を発揮するため、捩りばね定数は極力小さくする必要があり、この要求を満たしている。一方、エンジンの最大トルク以上の過大な入力に対しては、速やかに過大なトルクを吸収して捩り振動装置および変速機の強度と耐久性を確保するため、捩りばね定数は大きい必要があり、この要求も満たしている。 The torsional vibration reducing device exhibits a sufficient torsional vibration damping effect up to the maximum torque of the engine, and therefore the torsional spring constant needs to be as small as possible and satisfies this requirement. On the other hand, for excessive input exceeding the maximum torque of the engine, the torsion spring constant needs to be large in order to quickly absorb the excessive torque and ensure the strength and durability of the torsional vibration device and the transmission. This requirement is also satisfied.

この発明によれば、中間ばね受部８ｂが形成された中間部材８と、センタープレート３とは軸方向での同じ位置を占めており、中間部材８とセンタープレート３とは半径方向の外側と内側とに配置されているので、第１当接部８ｃと第２当接部３ｃとの形成が容易である。 According to the present invention, the intermediate member 8 in which the intermediate spring receiving portion 8b is formed and the center plate 3 occupy the same position in the axial direction, and the intermediate member 8 and the center plate 3 are radially outward. Therefore, the first contact portion 8c and the second contact portion 3c can be easily formed.

この発明によれば、連結ピン１７は半径方向でのセンタープレート３の第２ばね受部３ａの外側であって中間部材８の環状部８ａの内側に配置されているので、連結ピン１７がセンタープレート３や中間部材８に接触することはない。また、連結ピン１７は円周方向での中間ばね受部８ｂどうしの間に配置されているので、連結ピン１７が中間ばね受部８ｂに接触することもない。 According to the present invention, since the connecting pin 17 is disposed outside the second spring receiving portion 3a of the center plate 3 in the radial direction and inside the annular portion 8a of the intermediate member 8, the connecting pin 17 is centered. There is no contact with the plate 3 or the intermediate member 8. Further, since the connecting pin 17 is disposed between the intermediate spring receiving portions 8b in the circumferential direction, the connecting pin 17 does not contact the intermediate spring receiving portion 8b.

なお、本実施の形態では第２当接部を出力側回転部材に形成したが、入力側回転部材に形成してもよい。この場合は、第１当接部を円周方向へ突出させることなく軸方向へ突出させる一方、第２当接部を入力側回転部材の第２ばね受け部から円周方向へ突出させて形成すればよい。 In the present embodiment, the second contact portion is formed on the output side rotating member, but may be formed on the input side rotating member. In this case, the first contact portion is protruded in the axial direction without protruding in the circumferential direction, while the second contact portion is protruded in the circumferential direction from the second spring receiving portion of the input side rotation member. do it.

捩り振動低減装置に係り、（ａ）は（ｂ）のＡＢＣＤＥＯＦＧＨＩＪ断面図、（ｂ）は一方のサイドプレートの一部を破断して示す正面図（実施の形態）。FIG. 2A is a cross-sectional view of ABCDEOFGHHIJ in FIG. 2B, and FIG. 2B is a front view showing a part of one side plate in a cutaway state (embodiment). 捩り振動低減装置の捩り角度とトルクとの関係を示すグラフ（実施の形態）。The graph which shows the relationship between the twist angle of a torsional vibration reduction apparatus, and a torque (embodiment).

符号の説明Explanation of symbols

１，２…サイドプレート（入力側回転部材）
３…センタープレート（出力側回転部材）
３ａ…第２ばね受部
３ｃ…第２当接部
４，５…ばね（弾性部材）
６…スリット
７…第１ばね受部
８…フローティングイコライザ（中間部材）
８ａ…環状部
８ｂ…中間ばね受部
８ｃ…第１当接部
１７…連結ピン 1, 2 ... Side plate (input side rotating member)
3. Center plate (output side rotating member)
3a ... 2nd spring receiving part 3c ... 2nd contact part 4, 5 ... Spring (elastic member)
6 ... Slit 7 ... First spring receiving portion 8 ... Floating equalizer (intermediate member)
8a ... annular part 8b ... intermediate spring receiving part 8c ... first contact part 17 ... connecting pin

Claims

一対のサイドプレートと該一対のサイドプレートの間に相対回転可能に収容されたセンタープレートとのいずれか一方により構成され駆動源からの入力により回転する入力側回転部材と、他方により構成された出力側回転部材と、前記一対のサイドプレートの夫々の同じ位置に円周方向に沿ってスリットを形成することにより該スリット間に形成された複数の第１ばね受部と、該第１ばね受部と円周方向の同じ位置を占めると共に前記センタープレートから半径方向外側へ向かって突出する第２ばね受部と、前記第１ばね受部間であってかつ前記第２ばね受部間に円周方向に沿って直列配置された一対の弾性部材と、前記一対のサイドプレートの間であってかつ前記第２ばね受部の半径方向外側に配置された環状部と該環状部から半径方向内側へ向かって前記第２ばね受部間へ突出して前記一対の弾性部材の間に介在する中間ばね受部とを有する中間部材とを備えた捩り振動低減装置において、
前記中間ばね受部の基端部の円周方向両側に第１当接部を形成する一方、前記入力側回転部材の前記第１ばね受部または前記出力側回転部材の前記第２ばね受部には前記第１当接部に当接して前記一対の弾性部材の一方の圧縮を中断させる第２当接部を形成したことを特徴とする捩り振動低減装置。 An input-side rotating member that is constituted by one of a pair of side plates and a center plate that is accommodated between the pair of side plates so as to be relatively rotatable, and an output that is constituted by the other and rotated by an input from a drive source A plurality of first spring receivers formed between the slits by forming a slit along the circumferential direction at the same position of each of the side rotation member and the pair of side plates; and the first spring receivers And a second spring receiving portion that occupies the same position in the circumferential direction and projects radially outward from the center plate, and between the first spring receiving portion and the second spring receiving portion. A pair of elastic members arranged in series along the direction, an annular portion disposed between the pair of side plates and radially outside the second spring support portion, and radially inward from the annular portion In the torsional vibration reduction device including an intermediate member and an intermediate spring receiving portion headed by projecting between the second spring receiving portion interposed between said pair of elastic members to,
The first contact portion is formed on both sides in the circumferential direction of the base end portion of the intermediate spring receiving portion, while the first spring receiving portion of the input side rotating member or the second spring receiving portion of the output side rotating member. The torsional vibration reducing device is characterized in that a second abutting portion is formed which abuts on the first abutting portion and interrupts compression of one of the pair of elastic members.

請求項１に記載の捩り振動低減装置において、
前記第１当接部は前記中間ばね受部の基端部の円周方向両側から円周方向へ突出して形成される一方、前記第２当接部は前記センタープレートにおける前記第２ばね受部の半径方向外側であって円周方向両側に円周方向へ突出して形成されていることを特徴とする捩り振動低減装置。 The torsional vibration reducing device according to claim 1,
The first contact portion is formed to protrude from both sides in the circumferential direction of the proximal end portion of the intermediate spring receiving portion, while the second contact portion is the second spring receiving portion of the center plate. A torsional vibration reduction device characterized by being formed to protrude in the circumferential direction on both sides in the circumferential direction.

請求項１または２に記載の捩り振動低減装置において、
前記一対のサイドプレートどうしを軸方向に連結して結合する連結ピンが設けられ、該連結ピンの半径方向の位置は、前記中間部材の前記環状部と前記センタープレートの前記第２ばね受部との間であることを特徴とする捩り振動低減装置。 The torsional vibration reducing device according to claim 1 or 2,
A connecting pin for connecting and connecting the pair of side plates in the axial direction is provided, and the position of the connecting pin in the radial direction is set between the annular portion of the intermediate member and the second spring receiving portion of the center plate. A torsional vibration reducing device characterized by being between.