JP4381183B2 - Torsional vibration reduction device - Google Patents

Torsional vibration reduction device Download PDF

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JP4381183B2
JP4381183B2 JP2004072273A JP2004072273A JP4381183B2 JP 4381183 B2 JP4381183 B2 JP 4381183B2 JP 2004072273 A JP2004072273 A JP 2004072273A JP 2004072273 A JP2004072273 A JP 2004072273A JP 4381183 B2 JP4381183 B2 JP 4381183B2
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spring
torsional vibration
spring member
piston
rotating member
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JP2005257027A (en
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喜誉司 山本
裕樹 山本
誠二 桃井
達也 森下
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Valeo Kapec Japan KK
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Valeo Unisia Transmission KK
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers

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Description

本発明は、エンジンとトランスミッションとの間の動力伝達系等に介装されてその系の捩り振動を低減する捩り振動低減装置に関する。   The present invention relates to a torsional vibration reduction device that is interposed in a power transmission system or the like between an engine and a transmission and reduces the torsional vibration of the system.

捩り振動低減装置は、トルクコンバータ内のロックアップピストンとタービンハブとの間に介装され、入力側と出力側とが直結された状態であるロックアップ時における捩り振動を低減するものであり、ロックアップピストンに結合された入力側回転部材である保持プレートと、出力側回転部材である出力プレートとが円周方向においてばね部材を介して連結された構成となっている。   The torsional vibration reduction device is interposed between the lockup piston in the torque converter and the turbine hub, and reduces torsional vibration at the time of lockup in which the input side and the output side are directly connected. A holding plate, which is an input side rotating member coupled to the lockup piston, and an output plate, which is an output side rotating member, are connected via a spring member in the circumferential direction.

従来の捩り振動低減装置を特許文献１に示す。この捩り振動低減装置はオートマチック・トランスミッション用のものであり、ダンパとして使用されるスプリングを収容する空間を大きくするため、ホールドプレートには切り欠きが形成され、当該切り欠きの部分にスプリングを収容している。
特開２００２−１２２２１１号公報（（００２１）、図２〜５） A conventional torsional vibration reducing device is shown in Patent Document 1. This torsional vibration reduction device is for an automatic transmission. In order to increase the space for accommodating a spring used as a damper, a notch is formed in the hold plate, and the spring is accommodated in the notch. ing.
JP 200212221 A ((0021), FIGS. 2 to 5)

ところが、スプリングがロックアップピストンと直接に当接して摺動するため、ロックアップピストンにスプリングの摩耗痕が付いてヒステリシスが増加し、制振性能が低下する。   However, since the spring slides in direct contact with the lockup piston, the lockup piston is marked with wear marks on the spring, increasing the hysteresis and lowering the damping performance.

ホールドプレートには浸炭窒化処理等の高硬度の熱処理が施されているが、ロックアップピストンは摩擦ライニングを介してコンバータカバーと摩擦結合することになるために高い形状精度が要求され、そのためロックアップピストンにはガス軟膣化処理等の比較的硬度の低い熱処理が施され、耐摩耗性はホールドプレートよりも小さい。一方、ロックアップピストンにＳＫ材のシートなどの薄い高硬度シートを介在させることも考えられるが、部品点数が多くなり、コスト高になる。   The hold plate is heat-treated with high hardness such as carbonitriding, but the lock-up piston is frictionally coupled to the converter cover via the friction lining, so high shape accuracy is required. The piston is subjected to a heat treatment having a relatively low hardness such as a gas softening process, and the wear resistance is smaller than that of the hold plate. On the other hand, a thin high hardness sheet such as a sheet of SK material may be interposed in the lockup piston, but the number of parts increases and the cost increases.

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、相互に対向する入力側回転部材と出力側回転部材とのうちの前記入力側回転部材をロックアップピストンに結合すると共に、前記入力側回転部材の外周部にばね部材を収容する円弧状の切欠部を形成し、該切欠部の両端縁に円周方向から前記ばね部材を挟んで対向する一対のばね受部を設け、前記入力側回転部材には、前記切欠部の内周縁に、前記ばね部材の内周側を規制する内周規制部を設け、前記出力側回転部材には、円周方向で前記ばね受部と対応する位置に、前記入力側回転部材へ向かって突出するばね押圧部を形成し、前記ばね押圧部と前記ばね受部との間で前記ばね部材を圧縮しながら前記入力側回転部材と前記出力側回転部材との間でトルクの伝達を行なう捩り振動低減装置において、前記内周規制部は前記切欠部の内周縁から半径方向の外側へ突出させて形成し、前記内周規制部の先端部から半径方向の外側へ向かって、前記ばね部材が前記ロックアップピストン側へ移動するのを規制する側面規制部を折曲形成したことを特徴とする。 According to the first aspect of the present invention, the input-side rotating member of the input-side rotating member and the output-side rotating member facing each other is coupled to a lock-up piston, and a spring member is provided on the outer peripheral portion of the input-side rotating member. And a pair of spring receiving portions facing each other across the spring member from the circumferential direction are provided at both end edges of the notch portion, and the input-side rotating member includes the notch portion. An inner periphery restricting portion for restricting the inner periphery side of the spring member is provided on the inner peripheral edge of the output member, and the output side rotating member is connected to the input side rotating member at a position corresponding to the spring receiving portion in the circumferential direction. A spring pressing portion that protrudes toward the front, and torque is transmitted between the input-side rotating member and the output-side rotating member while compressing the spring member between the spring pressing portion and the spring receiving portion. in the torsional vibration damping system that performs, the inner peripheral restricting portion It is formed by projecting radially outward from the inner peripheral edge of the notch, and restricts the spring member from moving toward the lock-up piston from the distal end of the inner circumferential restricting portion toward the radially outer side. The side regulating portion to be bent is formed .

このような捩り振動低減装置では、入力側回転部材の切欠部に収容されたばね部材の内周側は、入力側回転部材の内周規制部によって規制され、ばね部材が圧縮される際に、ばね部材は内周規制部の先端部である側面規制部に対して擦れることになり、ばね部材と耐摩耗性の小さいロックアップピストンとの擦れは生じない。 In such a torsional vibration reducing device, the inner peripheral side of the spring member accommodated in the notch portion of the input side rotating member is regulated by the inner circumference regulating portion of the input side rotating member, and the spring member is compressed when the spring member is compressed. The member rubs against the side surface restricting portion, which is the tip of the inner periphery restricting portion, and there is no friction between the spring member and the lock-up piston with low wear resistance .

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、前記出力側回転部材に、前記ばね部材の前記ロックアップピストンとは反対側への移動を規制する第２側面規制部を設けたことを特徴とする。   According to a second aspect of the present invention, in the torsional vibration reducing device according to the first aspect, a second side surface restricting portion that restricts the output-side rotating member from moving the spring member to the side opposite to the lock-up piston. Is provided.

このような捩り振動低減装置では、ばね部材の内周側は、入力側回転部材の内周規制部によって規制され、ばね部材の両側は、入力側回転部材の側面規制部と出力側回転部材の第２側面規制部とによって規制される。   In such a torsional vibration reduction device, the inner circumferential side of the spring member is regulated by the inner circumferential regulating portion of the input side rotating member, and both sides of the spring member are the side regulating portion of the input side rotating member and the output side rotating member. It is regulated by the second side regulation part.

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、前記ばね受部には絞り加工を施し、該絞り加工した部分の近傍に、前記入力側回転部材を前記ロックアップピストンに結合するためのリベットを配置したことを特徴とする。   According to a third aspect of the present invention, in the torsional vibration reducing device according to the first or second aspect, the spring receiving portion is subjected to a drawing process, and the input side rotating member is locked to the lock in the vicinity of the drawn portion. A rivet for connecting to the up piston is arranged.

このような捩り振動低減装置では、ばね受け部を絞り加工したので、ばね部材が圧縮される際にばね受け部に大きな力が加わっても十分に耐えることができる。また、絞り加工するときには内部応力が生じるが、この内部応力はリベット用の孔を加工することで逃がすことができる。このため、入力側回転部材を熱処理すると変形するが、リベット用の孔の加工により、この変形が抑制される。   In such a torsional vibration reducing device, since the spring receiving portion is drawn, it can sufficiently withstand even if a large force is applied to the spring receiving portion when the spring member is compressed. Further, an internal stress is generated when the drawing process is performed, and this internal stress can be released by processing a hole for a rivet. For this reason, when the input side rotating member is heat-treated, it is deformed, but this deformation is suppressed by processing the rivet hole.

本発明に係る捩り振動低減装置によれば、入力側回転部材の切欠部に収容されたばね部材の内周側は、入力側回転部材の内周規制部によって規制され、ばね部材が圧縮される際に、ばね部材は内周規制部の先端部である側面規制部に対して擦れることになり、ばね部材がロックアップピストンに対して擦れることはない。従って、ロックアップピストンにばね部材の摩耗痕が付いたり、ヒステリシスが増加して制振性能が低下するようなことはない。   According to the torsional vibration reducing device of the present invention, the inner peripheral side of the spring member accommodated in the notch portion of the input side rotating member is regulated by the inner circumference regulating portion of the input side rotating member, and the spring member is compressed. In addition, the spring member rubs against the side surface restricting portion that is the tip of the inner periphery restricting portion, and the spring member does not rub against the lockup piston. Therefore, the wear-up mark of the spring member is not attached to the lock-up piston, and the damping performance is not deteriorated due to an increase in hysteresis.

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.

（ａ）実施の形態１
まず、実施の形態１について説明する。図１は自動変速機の前端部側に配置されるトルクコンバータのロックアップクラッチ部分の断面図である。エンジンのクランクシャフトは図示しないコンバータハウジングに結合されており、コンバータハウジングは、図示しないトルクコンバータを介して図示しないタービンハブに接続される一方、高速運転時等にコンバータハウジングをタービンハブと直結するためのロックアップピストン（ロックアップクラッチ４を構成する）１０および捩り振動低減装置５を介してタービンハブに接続されている。このタービンハブは、自動変速機の図示しない入力軸にスプライン結合されている。トルクコンバータ自体は周知のものであり、図示しないクランクシャフトからコンバータハウジングに入力されたトルクをポンプ，タービン間の流体の作用により、タービンハブに伝達する基本構成となっている。 (A) Embodiment 1
First, the first embodiment will be described. FIG. 1 is a cross-sectional view of a lock-up clutch portion of a torque converter disposed on the front end side of an automatic transmission. The crankshaft of the engine is coupled to a converter housing (not shown). The converter housing is connected to a turbine hub (not shown) via a torque converter (not shown), while the converter housing is directly connected to the turbine hub during high-speed operation. Are connected to the turbine hub via a lockup piston (which constitutes the lockup clutch 4) 10 and a torsional vibration reducing device 5. The turbine hub is splined to an input shaft (not shown) of the automatic transmission. The torque converter itself is well known, and has a basic configuration in which torque inputted from a crankshaft (not shown) to the converter housing is transmitted to the turbine hub by the action of fluid between the pump and the turbine.

捩り振動低減装置５は、ロックアップピストン１０に結合された略円板状の保持プレート（入力側回転部材）１３と、この保持プレート１３の外周縁部に保持された複数のばね部材１４と、外周縁部がばね部材１４を介して保持プレート１３に回転方向で連結された中間プレート（出力側回転部材）１６と、中間プレート１６に保持されると共にばね部材１４よりも内周側に配置された複数のばね部材１５と、外周縁部がばね部材１５を介して中間プレート１６に回転方向で連結された出力プレート８と、で構成されている。この出力プレート８の内周部が、タービンハブに結合される。   The torsional vibration reducing device 5 includes a substantially disc-shaped holding plate (input side rotating member) 13 coupled to the lock-up piston 10, a plurality of spring members 14 held on the outer peripheral edge of the holding plate 13, An outer peripheral edge portion is connected to the holding plate 13 via the spring member 14 in the rotation direction, and is held by the intermediate plate 16 and arranged closer to the inner peripheral side than the spring member 14. A plurality of spring members 15 and an output plate 8 whose outer peripheral edge is connected to the intermediate plate 16 via the spring member 15 in the rotational direction. An inner peripheral portion of the output plate 8 is coupled to the turbine hub.

ロックアップピストン１０の外周面の近傍には、軸方向へ移動して摩擦結合することにより前記コンバータハウジングと一体に回転するための摩擦ライニング６が貼着されている。ロックアップピストン１０は、熱処理による変形を抑制するために、ガス軟窒化等の硬度の低い熱処理が施されている。   In the vicinity of the outer peripheral surface of the lock-up piston 10, a friction lining 6 is attached so as to rotate integrally with the converter housing by moving in the axial direction and frictionally coupling. The lockup piston 10 is subjected to heat treatment with low hardness such as gas soft nitriding in order to suppress deformation due to heat treatment.

前記保持プレート１３の構成を図２に示す。保持プレート１３は、中心部を繰り抜いた形状であり、ロックアップクラッチ４を構成するロックアップピストン１０に一体に結合されている。保持プレート１３の外周縁部には、径方向に沿って略等間隔に円弧状の切欠部１７が形成され、隣り合う切欠部１７どうしの間の部分が主ばね受部１８を構成している。主ばね受部１８の部分は、強度を上げるために図２（ｂ）に示すように、円弧状に絞り加工が施されている。そして、この切欠部１７にばね部材１４を収容することで、一対の主ばね受部１８の間にばね部材１４を配置した状態になっている。   The structure of the holding plate 13 is shown in FIG. The holding plate 13 has a shape in which the center portion is pulled out, and is integrally coupled to the lockup piston 10 constituting the lockup clutch 4. In the outer peripheral edge of the holding plate 13, arc-shaped notches 17 are formed at substantially equal intervals along the radial direction, and a portion between adjacent notches 17 constitutes a main spring receiving portion 18. . As shown in FIG. 2B, the main spring receiving portion 18 is drawn into an arc shape to increase the strength. The spring member 14 is accommodated in the notch 17 so that the spring member 14 is disposed between the pair of main spring receiving portions 18.

ばね部材１４の（保持プレート１３に対しての）内周側を規制するために、前記切欠部１７における保持プレート１３の内側から外周へ向かって絞り加工により内周規制部１９が立ち上げられ、内周規制部１９の先端部を、ばね部材１４のロックアップピストン１０側の側面へ向かって折曲させることで、側面規制部１９ａが構成されている。また、ばね部材１４の外周側を規制するために、保持プレート１３の外周面近傍を軸方向に沿わせて絞り加工することで、ばね部材１４の外側を覆うようにして外周規制部２０が形成されている。切欠部１７の外側には、ばね部材１４が切欠部１７から飛び出ないようにするための主側面規制部２０ｂが形成され、更に、外周規制部２０の先端を内周側へ向かって絞り加工することで、ロックアップピストン１０とは反対側へばね部材１４が飛び出ないようにするための主側面ディストリクト部２０ａが形成されている。なお、便宜上、バネ部材１４を規制する規制部のうちの、図１（ｂ）におけるバネ部材１４の左側のものを規制部と称し、右側に形成されるものをディストリクト部と称することにする。このほか、円周方向での主ばね受部１８と対応する位置には、主側面ディストリクト部２０ａの部分を内周側へ向かって突出させて補助ばね受部２１が形成されている。   In order to regulate the inner peripheral side (relative to the holding plate 13) of the spring member 14, the inner peripheral regulating portion 19 is raised by drawing from the inside of the holding plate 13 to the outer circumference in the notch portion 17, The side regulating part 19a is configured by bending the tip of the inner circumference regulating part 19 toward the side face of the spring member 14 on the lockup piston 10 side. Further, in order to regulate the outer peripheral side of the spring member 14, the outer peripheral regulating portion 20 is formed so as to cover the outside of the spring member 14 by drawing the vicinity of the outer peripheral surface of the holding plate 13 along the axial direction. Has been. A main side surface restricting portion 20b for preventing the spring member 14 from jumping out of the notched portion 17 is formed outside the notched portion 17, and further, the tip of the outer periphery restricting portion 20 is drawn toward the inner peripheral side. In this way, a main side surface district portion 20a for preventing the spring member 14 from jumping out to the side opposite to the lock-up piston 10 is formed. For convenience, among the restricting portions that restrict the spring member 14, the left side of the spring member 14 in FIG. 1B is referred to as a restricting portion, and the one formed on the right side is referred to as a district portion. . In addition, an auxiliary spring receiving portion 21 is formed at a position corresponding to the main spring receiving portion 18 in the circumferential direction by projecting a portion of the main side surface district portion 20a toward the inner peripheral side.

前記のように、主ばね受部１８の部分は、ばね部材１４の端面との接触面積を増やしかつ強度を上げるために円弧状に絞り加工が施されている。そして、円周方向での主ばね受部１８と対応する位置の中心側に、保持プレート１３をロックアップピストン１０に結合するための第１リベット２２の孔２３が配置されている。これは、主ばね受部１８を絞り加工したときに内部応力が生じるが、この内部応力は第１リベット２２用の孔２３を加工することで逃がすことができ、保持プレート１３を熱処理した後に生じる変形が抑制されるように考慮したものである。   As described above, the main spring receiving portion 18 is drawn in an arc shape in order to increase the contact area with the end face of the spring member 14 and increase the strength. A hole 23 of the first rivet 22 for connecting the holding plate 13 to the lock-up piston 10 is disposed on the center side of the position corresponding to the main spring receiving portion 18 in the circumferential direction. This is because internal stress is generated when the main spring receiving portion 18 is drawn. This internal stress can be released by processing the hole 23 for the first rivet 22 and is generated after the holding plate 13 is heat-treated. This is so considered that the deformation is suppressed.

保持プレート１３はばね部材１４を圧縮したり、ばね部材１４と擦れたりすることから、保持プレート１３には高い硬度や高い強度が求められ、保持プレート１３には浸炭窒化処理等が施される。   Since the holding plate 13 compresses the spring member 14 or rubs against the spring member 14, the holding plate 13 is required to have high hardness and high strength, and the holding plate 13 is subjected to carbonitriding.

中間プレート１６は、図３に示すリテーニングプレート２４と、図４に示すリテーニングプレート２５とを結合して構成される。リテーニングプレート２４には、外周部に円周方向へ等間隔に複数のばね押圧部２６が形成されている。このばね押圧部２６は、円周方向で前記主ばね受部１８と対応する位置を占めるものであり、ばね部材１４の双方の端面の近傍から、保持プレート１３へ向かって軸方向へ突出している。ばね押圧部２６の付け根の部分にはアール部２６ａが形成されている。これは、ばね押圧部２６がばね部材１４から大きな曲げモーメントを受けるので、これに耐えられるように強度を高めるためである。   The intermediate plate 16 is configured by combining a retaining plate 24 shown in FIG. 3 and a retaining plate 25 shown in FIG. In the retaining plate 24, a plurality of spring pressing portions 26 are formed on the outer peripheral portion at equal intervals in the circumferential direction. The spring pressing portion 26 occupies a position corresponding to the main spring receiving portion 18 in the circumferential direction, and protrudes in the axial direction toward the holding plate 13 from the vicinity of both end faces of the spring member 14. . A rounded portion 26 a is formed at the base portion of the spring pressing portion 26. This is because the spring pressing portion 26 receives a large bending moment from the spring member 14, and thus increases the strength so that it can withstand this.

ばね押圧部２６どうしの間にはばね押え２７が形成されている。ばね押え２７はばね部材１４の内周方向と反ロックアップピストン１０方向を規制するもので、図に示すようにばね部材１４の内周部分に斜めに当接して内周部分を規制することにより、両方向の規制を可能にしている。以下、このばね押え２７を内周方向の規制を行う機能部位として呼ぶときは内周ディストリクト部２７ａ、反ロックアップピストン１０方向の規制を行う機能部位として呼ぶときは側面ディストリクト部（第２側面規制部）２７ｂ、総称して呼ぶときはばね押え２７という。なお、このばね押え２７はばね部材１４の内周側から反ロックアップピストン１０側へ沿うようにして設け、規制時の接触面積を増やすことによって、耐摩耗性を向上させてもよい。   A spring retainer 27 is formed between the spring pressing portions 26. The spring retainer 27 regulates the inner circumferential direction of the spring member 14 and the anti-lock-up piston 10 direction, and as shown in the figure, it abuts on the inner circumferential portion of the spring member 14 obliquely to regulate the inner circumferential portion. , Allowing regulation in both directions. Hereinafter, when this spring retainer 27 is called as a functional part for regulating the inner circumferential direction, the inner circumferential part 27a, and when called as a functional part for regulating the anti-lockup piston 10 direction, a side district part (second (Side regulating portion) 27b, which is collectively referred to as a spring retainer 27. The spring retainer 27 may be provided so as to extend from the inner peripheral side of the spring member 14 to the anti-lock-up piston 10 side, and the wear resistance may be improved by increasing the contact area at the time of regulation.

リテーニングプレート２４の内周側には、内周側のばね部材１５を支持するための収容窓２８が、円周方向に沿って略等間隔に形成されている。収容窓２８は略円弧状に形成されており、ばね部材１５の収容空間を形成するために、収容窓２８の内周側および外周側の縁部は外側へ斜めに起こしてばね押え２８ａ，２８ｂが形成されている。これにより、隣り合う収容窓２８どうしの間の部分がばね部材１５の両端を受けるばね受部２９として機能する。   On the inner peripheral side of the retaining plate 24, receiving windows 28 for supporting the inner peripheral spring member 15 are formed at substantially equal intervals along the circumferential direction. The housing window 28 is formed in a substantially arc shape, and in order to form a housing space for the spring member 15, the edges on the inner peripheral side and the outer peripheral side of the housing window 28 are raised obliquely outward and the spring retainers 28 a and 28 b. Is formed. Thereby, the part between the adjacent accommodation windows 28 functions as a spring receiving portion 29 that receives both ends of the spring member 15.

他方のリテーニングプレート２５は図４に示すように構成されており、リテーニングプレート２４と異なる点は、ばね押圧部２６とばね押え２７とが形成されていないことである。   The other retaining plate 25 is configured as shown in FIG. 4, and is different from the retaining plate 24 in that the spring pressing portion 26 and the spring retainer 27 are not formed.

出力プレート８の構成を図５に示す。半径方向および円周方向で前記収容窓２８と対応する位置に、ばね部材１５を収容するための収容窓３２が形成されている。これにより、隣り合う収容窓３２どうしの間の部分が、ばね部材１５の両端を押圧するばね押圧部３４として機能する。そして、先に述べた図示しないタービンハブと結合するための孔３３が内周面の近傍に複数形成されている。   The configuration of the output plate 8 is shown in FIG. An accommodation window 32 for accommodating the spring member 15 is formed at a position corresponding to the accommodation window 28 in the radial direction and the circumferential direction. Thereby, the part between adjacent accommodation windows 32 functions as a spring pressing part 34 that presses both ends of the spring member 15. A plurality of holes 33 for coupling to the turbine hub (not shown) described above are formed in the vicinity of the inner peripheral surface.

この出力プレート８をリテーニングプレート２４とリテーニングプレート２５との間に挟んだ状態で、リテーニングプレート２４，リテーニングプレート２５における収容窓２８の外側に形成された孔３０に第２リベット３１を挿通して両者が結合されている。これにより、図１に示すようにばね部材１５は収容窓２８，３２，２８に跨って収容されており、中間プレート１６と出力プレート８とが相対的に回転すると、ばね受部２９とばね押圧部３４との間に挟まれてばね部材１５が圧縮される。   In a state where the output plate 8 is sandwiched between the retaining plate 24 and the retaining plate 25, the second rivet 31 is inserted into the retaining plate 24 and the hole 30 formed outside the receiving window 28 in the retaining plate 25. Both are connected through the insertion. As a result, as shown in FIG. 1, the spring member 15 is accommodated across the accommodation windows 28, 32, 28, and when the intermediate plate 16 and the output plate 8 rotate relatively, the spring receiving portion 29 and the spring press The spring member 15 is compressed by being sandwiched between the portions 34.

図３において、ばね押え２７と孔３０と収容窓２８とが円周方向で同じ位置に配置されており、図１（ａ）に示すように、第１リベット２２と第２リベット３１とが円周方向に交互に配置されていることになる。また、リテーニングプレート２４の剛性を高くするために、図３に示すように半径方向における収容窓２８と孔３０との間には、絞り部１２が形成されている。これにより、リテーニングプレート２４がばね部材１５からトルク反力を受ける際に、ばね押圧部２６の変形が抑えられて性能劣化が防止される。   In FIG. 3, the spring retainer 27, the hole 30, and the receiving window 28 are arranged at the same position in the circumferential direction, and the first rivet 22 and the second rivet 31 are circular as shown in FIG. They are alternately arranged in the circumferential direction. In addition, in order to increase the rigidity of the retaining plate 24, a throttle portion 12 is formed between the receiving window 28 and the hole 30 in the radial direction as shown in FIG. Thereby, when the retaining plate 24 receives the torque reaction force from the spring member 15, the deformation of the spring pressing portion 26 is suppressed and the performance deterioration is prevented.

ばね部材１４は、図１（ｂ）に示すように親ばね１４ａと親ばね１４ａの内部に収容した子ばね１４ｂとからなる入れ子ばねで構成されている。子ばね１４ｂは親ばね１４ａよりも短く構成されており、親ばね１４ａと子ばね１４ｂとの双方を確実に圧縮できるように、親ばね１４ａの両端にはリテーナが装着されている。リテーナの形状は、円板の片面に、親ばね１４ａの内部に嵌合するための円柱状の凸部を形成したものである。一方、ばね部材１５は、親ばね１５ａと親ばね１５ａの内部に収容した子ばね１５ｂとからなる入れ子ばねで構成されている。その他の構成についてはばね部材１４と同じなので、説明を省略する。   As shown in FIG. 1B, the spring member 14 is configured by a nested spring including a parent spring 14a and a child spring 14b accommodated in the parent spring 14a. The child spring 14b is configured to be shorter than the parent spring 14a, and retainers are attached to both ends of the parent spring 14a so that both the parent spring 14a and the child spring 14b can be reliably compressed. The shape of the retainer is such that a cylindrical convex portion for fitting inside the parent spring 14a is formed on one side of the disc. On the other hand, the spring member 15 is configured by a nested spring including a parent spring 15a and a child spring 15b accommodated in the parent spring 15a. Since other configurations are the same as those of the spring member 14, the description thereof is omitted.

次に、捩り振動低減装置の作用を説明する。クランクシャフトの回転によってコンバータハウジングが回転すると、トルクコンバータが回転し、その動力がタービンハブからトランスミッションへと伝達する。この状態からクランクシャフトの回転速度等が設定した制御条件に達すると、支持壁に設けられた油孔から図１（ｂ）のロックアップピストン１０の右側に圧油が導入され、その油圧によってロックアップピストン１０が左側へ押圧される。すると、このロックアップピストン１０がコンバータハウジングに押し付けられ、コンバータハウジングの動力がロックアップピストン１０を介して捩り振動低減装置５に伝達される。   Next, the operation of the torsional vibration reducing device will be described. When the converter housing is rotated by the rotation of the crankshaft, the torque converter is rotated, and the power is transmitted from the turbine hub to the transmission. From this state, when the crankshaft rotational speed or the like reaches a set control condition, pressure oil is introduced to the right side of the lock-up piston 10 in FIG. 1B from the oil hole provided in the support wall, and is locked by the hydraulic pressure. The up piston 10 is pressed to the left. Then, the lockup piston 10 is pressed against the converter housing, and the power of the converter housing is transmitted to the torsional vibration reducing device 5 via the lockup piston 10.

捩り振動低減装置５では、ロックアップピストン１０と一体の保持プレート１３の回転力は、ばね部材１４を介して中間プレート１６に伝達され、更に中間プレート１６からばね部材１５を介して出力プレート８へ伝わる。   In the torsional vibration reducing device 5, the rotational force of the holding plate 13 integrated with the lockup piston 10 is transmitted to the intermediate plate 16 through the spring member 14, and further from the intermediate plate 16 to the output plate 8 through the spring member 15. It is transmitted.

このとき、ばね部材１４の両端部が保持プレート１３の一対の主ばね受部１８（および補助ばね受部２１）に挟まれ、かつ中間プレート１６の一対のばね押圧部２６に挟まれている。このため、保持プレート１３と中間プレート１６とが相対的に回転すると、ばね部材１４のいずれか一方側の端面が保持プレート１３の主ばね受部１８に当接すると共に他方側の端部が中間プレート１６のばね押圧部２６に当接し、保持プレート１３と中間プレート１６との間でばね部材１４が圧縮される。   At this time, both end portions of the spring member 14 are sandwiched between the pair of main spring receiving portions 18 (and the auxiliary spring receiving portion 21) of the holding plate 13 and between the pair of spring pressing portions 26 of the intermediate plate 16. For this reason, when the holding plate 13 and the intermediate plate 16 are relatively rotated, either one end surface of the spring member 14 abuts on the main spring receiving portion 18 of the holding plate 13 and the other end portion is the intermediate plate. The spring member 14 abuts on the 16 spring pressing portions 26, and the spring member 14 is compressed between the holding plate 13 and the intermediate plate 16.

同様にして、ばね部材１５の両端部が中間プレート１６の一対のばね受部２９に挟まれ、かつ出力プレート８の一対のばね押圧部３４に挟まれている。このため、中間プレート１６と出力プレート８とが相対的に回転すると、ばね部材１５のいずれか一方側の端面が中間プレート１６のばね受部２９に当接すると共に他方側の端部が出力プレート８のばね押圧部３４に当接し、中間プレート１６と出力プレート８との間でばね部材１５が圧縮される。   Similarly, both end portions of the spring member 15 are sandwiched between a pair of spring receiving portions 29 of the intermediate plate 16 and sandwiched between a pair of spring pressing portions 34 of the output plate 8. For this reason, when the intermediate plate 16 and the output plate 8 are relatively rotated, the end surface on one side of the spring member 15 contacts the spring receiving portion 29 of the intermediate plate 16 and the end portion on the other side is the output plate 8. The spring member 15 is compressed between the intermediate plate 16 and the output plate 8.

保持プレート１３と中間プレート１６との相対的な捩れに応じてばね部材１４が圧縮変形し、かつ中間プレート１６と出力プレート８との相対的な捩れに応じてばね部材１５が圧縮変形することにより、伝達系の捩り振動を吸収する。つまり、保持プレート１３と出力プレート８との間に、ばね部材１４とばね部材１５とを直列に介在させたのと等価になる。   The spring member 14 is compressed and deformed according to the relative twist of the holding plate 13 and the intermediate plate 16, and the spring member 15 is compressed and deformed according to the relative twist of the intermediate plate 16 and the output plate 8. Absorbs torsional vibrations in the transmission system. That is, it is equivalent to the spring member 14 and the spring member 15 being interposed in series between the holding plate 13 and the output plate 8.

ここで、ばね部材１４の内周側は、図２の内周規制部１９と図３のばね押え２７の中間部の内周ディストリクト部２７ａとの双方によって規制される。ばね部材１４の外周側は、図２の外周規制部２０によって規制されている。側面の一方側は図２の主側面規制部２０ｂと側面規制部１９ａとの双方によって規制され、他方側は図２の主側面ディストリクト部２０ａと図３のばね押え２７の先端の側面ディストリクト部２７ｂとの双方によって規制されている。ばね部材１４が圧縮される際にばね部材１４は側面規制部１９ａと擦れることになり、ロックアップピストン１０と擦れることはない。   Here, the inner circumferential side of the spring member 14 is regulated by both the inner circumferential regulating portion 19 in FIG. 2 and the inner circumferential district portion 27a at the intermediate portion of the spring retainer 27 in FIG. The outer peripheral side of the spring member 14 is regulated by the outer circumference regulating unit 20 in FIG. One side of the side surface is regulated by both the main side regulating portion 20b and the side regulating portion 19a in FIG. 2, and the other side is the side district at the tip of the main side district portion 20a in FIG. 2 and the spring retainer 27 in FIG. It is regulated by both the part 27b. When the spring member 14 is compressed, the spring member 14 rubs against the side surface restricting portion 19 a and does not rub against the lock-up piston 10.

第１リベット２２で結合されたロックアップピストン１０と保持プレート１３とばね部材１４とを外周サブアッセンブリーとし、第２リベット３１で結合された中間プレート１６と出力プレート８とばね部材１５とを内周サブアッセンブリーとしたときに、外周サブアッセンブリーと内周サブアッセンブリーとの組み付けは、ばね押圧部２６をばね部材１４どうしの間に軸方向から挿入させて、軸方向に結合させることになるので、外周サブアッセンブリーと内周サブアッセンブリーとは軸方向に着脱可能となる。   The lockup piston 10, the holding plate 13, and the spring member 14 coupled by the first rivet 22 serve as an outer peripheral subassembly, and the intermediate plate 16, the output plate 8, and the spring member 15 coupled by the second rivet 31 are coupled to the inner periphery. When the sub-assembly is used, the assembly of the outer peripheral sub-assembly and the inner peripheral sub-assembly is performed by inserting the spring pressing portion 26 between the spring members 14 from the axial direction and coupling them in the axial direction. The subassembly and the inner peripheral subassembly can be attached and detached in the axial direction.

ばね部材１４の内周側を規制する内周ディストリクト部２７ａを形成したので、保持プレート１３のみに内周規制部を形成してばね部材１５のロックアップピストン１０とは反対側の側面を規制する部分を設けた場合に比べ、内周規制部への干渉防止のために行うバネ押圧部２６の反ロックアップピストン１０方向への逃がしの量を少なくすることができる。   Since the inner peripheral district portion 27a for restricting the inner peripheral side of the spring member 14 is formed, the inner peripheral restricting portion is formed only on the holding plate 13 and the side surface of the spring member 15 opposite to the lockup piston 10 is restricted. Compared with the case where the portion to be provided is provided, it is possible to reduce the amount of escape of the spring pressing portion 26 toward the anti-lock-up piston 10 in order to prevent interference with the inner periphery regulating portion.

また、中間プレート１６のばね押え２７にロックアップピストン１０とは反対側のばね部材１４の側面を押える側面ディストリクト部２７ｂを形成したので、ばね部材１４の保持が安定する。   Further, the side retainer 27b for pressing the side surface of the spring member 14 opposite to the lock-up piston 10 is formed on the spring retainer 27 of the intermediate plate 16, so that the holding of the spring member 14 is stabilized.

中間プレート１６を構成する一対のリテーニングプレート２４，２５のうちの保持プレート１３とは反対側のリテーニングプレート２４にばね押圧部２６，ばね押え２７を形成したので、図１（ｂ）に示すように、保持プレート１３の絞りを形成した主ばね受部１８との干渉を回避するための大きな曲げ部分を円周方向での第２リベット３１の近傍に設けずに済む。また、円周方向での第２リベット３１の近傍に大きな曲げ部分を設けずに済むことから、リベッティングによる第２リベット３１用の孔３０の亀裂発生を防止できる。   Since the spring pressing portion 26 and the spring retainer 27 are formed on the retaining plate 13 on the opposite side of the holding plate 13 of the pair of retaining plates 24 and 25 constituting the intermediate plate 16, it is shown in FIG. Thus, it is not necessary to provide a large bent portion in the vicinity of the second rivet 31 in the circumferential direction in order to avoid interference with the main spring receiving portion 18 in which the aperture of the holding plate 13 is formed. In addition, since it is not necessary to provide a large bent portion in the vicinity of the second rivet 31 in the circumferential direction, it is possible to prevent cracks in the holes 30 for the second rivet 31 due to riveting.

（ｂ）実施の形態２
次に、実施の形態２を図６に基づいて説明する。なお、実施の形態１と同一部分には同一符号を付し、重複する部分については説明を省略する。 (B) Embodiment 2
Next, the second embodiment will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the same part as Embodiment 1, and description is abbreviate | omitted about the overlapping part.

実施の形態１の捩り振動低減装置は、ばね部材１４の内周側を、保持プレート１３の内周規制部１９と中間プレート１６のばね押え２７の内周ディストリクト部２７ａとの双方で規制するものであるが、実施の形態２は、図６に示すように内周規制部１９を反ロックアップピストン１０側へ張り出させることにより、ばね押え２７を省略したものである。   In the torsional vibration reduction device of the first embodiment, the inner peripheral side of the spring member 14 is restricted by both the inner peripheral restricting portion 19 of the holding plate 13 and the inner peripheral district portion 27a of the spring retainer 27 of the intermediate plate 16. However, in the second embodiment, the spring retainer 27 is omitted by projecting the inner periphery restricting portion 19 toward the anti-lock-up piston 10 as shown in FIG.

なお、ばね押え２７の省略のためには、必ず内周規制部１９を反ロックアップピストン１０側へ張り出さなければならないというわけではなく、例えば主側面ディストリクト部２０ａの内周へ向かう量が十分であってばね部材１４の飛び出しが抑えられる場合は、内周規制部１９の張り出しを設けることなくばね押え２７を省略することができる。   In order to omit the spring retainer 27, the inner periphery restricting portion 19 does not necessarily have to protrude to the anti-lock-up piston 10 side. For example, the amount toward the inner periphery of the main side surface restrict portion 20a is not limited. If it is sufficient and the spring member 14 can be prevented from popping out, the spring retainer 27 can be omitted without providing an overhang of the inner periphery restricting portion 19.

（ｃ）実施の形態３
最後に、実施の形態３を図７に基づいて説明する。なお、実施の形態１と同一部分には同一符号を付し、重複する部分については説明を省略する。 (C) Embodiment 3
Finally, Embodiment 3 will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the same part as Embodiment 1, and description is abbreviate | omitted about the overlapping part.

この実施の形態は、ばね部材１５と中間プレート１６とを廃止してばね部材を外側のみとし、保持プレート１３からばね部材１４を介して直接に出力プレート３５に回転力が伝わるようにしたものである。このため、出力プレート３５の外周面の近傍には図３（ｂ）と同様にばね押圧部３６，ばね押え３７が形成され、内周面の近傍にはタービンハブと結合するための孔３８が形成されている。   In this embodiment, the spring member 15 and the intermediate plate 16 are abolished so that the spring member is only outside, and the rotational force is transmitted directly from the holding plate 13 to the output plate 35 via the spring member 14. is there. Therefore, a spring pressing portion 36 and a spring retainer 37 are formed in the vicinity of the outer peripheral surface of the output plate 35 as in FIG. 3B, and a hole 38 for coupling with the turbine hub is formed in the vicinity of the inner peripheral surface. Is formed.

なお、本発明は実施の形態で説明した構成に限るものではなく、捩り振動低減装置を適用する場所はトルクコンバータ内に限らず、トルクコンバータの外部やトルクコンバータを採用しない車両の他の動力伝達部に適用しても良い。更に、実施の形態では単板式のクラッチを用いたものについて示したが、多板式のクラッチや、その他の構成のクラッチを用いたものでもよい。   Note that the present invention is not limited to the configuration described in the embodiment, and the place where the torsional vibration reducing device is applied is not limited to the inside of the torque converter, and other power transmission of the vehicle that does not employ the torque converter outside the torque converter. It may be applied to the part. Furthermore, in the embodiment, the single-plate clutch is used, but a multi-plate clutch or other configuration clutch may be used.

捩り振動低減装置に係り、（ａ）は一部破断して示す正面図、（ｂ）は（ａ）のＡ−Ａ矢視図（実施の形態１）。FIG. 4A is a front view showing a torsional vibration reduction device, with partly broken, and FIG. 5B is an AA arrow view of (a) (Embodiment 1). 捩り振動低減装置の保持プレートに係り、（ａ）は正面図、（ｂ）は（ａ）のＢ−Ｂ矢視図（実施の形態１）。It is related with the holding | maintenance plate of a torsional vibration reduction apparatus, (a) is a front view, (b) is the BB arrow line view of (a) (Embodiment 1). 捩り振動低減装置の一方のリテーニングプレートに係り、（ａ）は正面図、（ｂ）は（ａ）のＣ−Ｃ矢視図（実施の形態１）。FIG. 5A is a front view of a retaining plate of the torsional vibration reducing device, and FIG. 捩り振動低減装置の他方のリテーニングプレートに係り、（ａ）は正面図、（ｂ）は（ａ）のＤ−Ｄ矢視図（実施の形態１）。FIG. 5A is a front view of the other retaining plate of the torsional vibration reducing device, and FIG. 捩り振動低減装置の出力プレートに係り、（ａ）は正面図、（ｂ）は（ａ）のＥ−Ｅ矢視図（実施の形態１）。It relates to the output plate of the torsional vibration reducing device, (a) is a front view, (b) is an EE arrow view of (a) (Embodiment 1). 捩り振動低減装置の要部を示す断面図（実施の形態２）。Sectional drawing which shows the principal part of a torsional vibration reduction apparatus (Embodiment 2). 捩り振動低減装置に係り、（ａ）は一部破断して示す正面図、（ｂ）は（ａ）のＦ−Ｆ矢視図（実施の形態３）。(A) is a partially broken front view showing a torsional vibration reducing device, and (b) is a view taken along the line FF of (a) (Embodiment 3).

符号の説明Explanation of symbols

１０…ロックアップピストン
１２…絞り部
１３…保持プレート（入力側回転部材）
１４，１５…ばね部材
１６…中間プレート（出力側回転部材）
１７…切欠部
１８…主ばね受部
１９…内周規制部
１９ａ…側面規制部
２２…第１リベット
２７…ばね押え
２７ａ…内周ディストリクト部
２７ｂ…側面ディストリクト部（第２側面規制部）
DESCRIPTION OF SYMBOLS 10 ... Lock-up piston 12 ... Restriction part 13 ... Holding plate (input side rotation member)
14, 15 ... Spring member 16 ... Intermediate plate (output side rotating member)
DESCRIPTION OF SYMBOLS 17 ... Notch part 18 ... Main spring receiving part 19 ... Inner periphery control part 19a ... Side surface control part 22 ... 1st rivet 27 ... Spring retainer 27a ... Inner periphery district part 27b ... Side surface part part (2nd side control part)

Claims (3)

相互に対向する入力側回転部材と出力側回転部材とのうちの前記入力側回転部材をロックアップピストンに結合すると共に、前記入力側回転部材の外周部にばね部材を収容する円弧状の切欠部を形成し、該切欠部の両端縁に円周方向から前記ばね部材を挟んで対向する一対のばね受部を設け、前記入力側回転部材には、前記切欠部の内周縁に、前記ばね部材の内周側を規制する内周規制部を設け、
前記出力側回転部材には、円周方向で前記ばね受部と対応する位置に、前記入力側回転部材へ向かって突出するばね押圧部を形成し、前記ばね押圧部と前記ばね受部との間で前記ばね部材を圧縮しながら前記入力側回転部材と前記出力側回転部材との間でトルクの伝達を行なう捩り振動低減装置において、
前記内周規制部は前記切欠部の内周縁から半径方向の外側へ突出させて形成し、前記内周規制部の先端部から半径方向の外側へ向かって、前記ばね部材が前記ロックアップピストン側へ移動するのを規制する側面規制部を折曲形成したことを特徴とする捩り振動低減装置。 An arc-shaped cutout portion that couples the input-side rotation member of the input-side rotation member and the output-side rotation member facing each other to a lock-up piston, and accommodates a spring member on the outer peripheral portion of the input-side rotation member And a pair of spring receiving portions facing each other with the spring member interposed therebetween in the circumferential direction are provided at both end edges of the notch portion, and the input side rotating member is provided with the spring member on the inner peripheral edge of the notch portion. An inner circumference restricting part that regulates the inner circumference side of the
A spring pressing portion protruding toward the input-side rotating member is formed on the output-side rotating member at a position corresponding to the spring receiving portion in the circumferential direction, and the spring-pressing portion and the spring-receiving portion In the torsional vibration reduction device for transmitting torque between the input side rotating member and the output side rotating member while compressing the spring member between ,
The inner circumference restricting portion is formed to protrude radially outward from the inner peripheral edge of the notch, and the spring member is located on the lock-up piston side from the tip of the inner circumference restricting portion toward the radially outer side. torsional vibration damping system, characterized in that the bending form side regulating portion for regulating the movement of the. 請求項１に記載の捩り振動低減装置において、前記出力側回転部材に、前記ばね部材の前記ロックアップピストンとは反対側への移動を規制する第２側面規制部を設けたことを特徴とする捩り振動低減装置。   The torsional vibration reduction device according to claim 1, wherein the output-side rotating member is provided with a second side surface regulating portion that regulates movement of the spring member to the side opposite to the lock-up piston. Torsional vibration reduction device. 請求項１または２に記載の捩り振動低減装置において、前記ばね受部には絞り加工を施し、該絞り加工した部分の近傍に、前記入力側回転部材を前記ロックアップピストンに結合するためのリベットを配置したことを特徴とする捩り振動低減装置。   The torsional vibration reduction device according to claim 1 or 2, wherein the spring receiving portion is subjected to drawing processing, and a rivet for coupling the input side rotating member to the lockup piston in the vicinity of the drawn portion. A torsional vibration reducing device characterized by comprising:
JP2004072273A 2004-03-15 2004-03-15 Torsional vibration reduction device Expired - Lifetime JP4381183B2 (en)

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JP2002122211A (en) * 2000-10-11 2002-04-26 Exedy Corp Lock-up device of torque converter
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