JPH0540644U - Power transmission device for automatic transmission - Google Patents
Power transmission device for automatic transmissionInfo
- Publication number
- JPH0540644U JPH0540644U JP8865991U JP8865991U JPH0540644U JP H0540644 U JPH0540644 U JP H0540644U JP 8865991 U JP8865991 U JP 8865991U JP 8865991 U JP8865991 U JP 8865991U JP H0540644 U JPH0540644 U JP H0540644U
- Authority
- JP
- Japan
- Prior art keywords
- diameter portion
- small diameter
- large diameter
- power transmission
- transmission device
- 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
- 230000005540 biological transmission Effects 0.000 title claims description 27
- 238000005452 bending Methods 0.000 abstract description 10
- 230000002159 abnormal effect Effects 0.000 abstract description 4
- 230000002093 peripheral effect Effects 0.000 description 16
- 230000008878 coupling Effects 0.000 description 7
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 210000000078 claw Anatomy 0.000 description 5
- 229910000831 Steel Inorganic materials 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000010959 steel Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 2
- 238000007796 conventional method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000007858 starting material Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16H2045/0231—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 arranged in series
Landscapes
- Springs (AREA)
Abstract
(57)【要約】
【目的】 捩り振動及び曲げ振動を吸収でき、これら振
動に起因する車室内のこもり音等の異音をより一層低減
化する。
【構成】 クランクシャフト２５に固定される入力部材
１とトルクコンバータ２７のコンバータハウジング２８
に固定される出力部材１３とを所定角度相対回動できる
ように組み付け、入力部材１と出力部材１３とを複数の
ばね部材１６で回動方向に弾性的に連繋してある。入力
部材１は、小径部２と大径部３とに分割してあり、これ
ら小径部２と大径部３とをゴム状弾性部材１０で連繋す
ると共に、小径部２と大径部３との間に両者の相対回動
を規制するストッパ１２を形成してある。
(57) [Abstract] [Purpose] It is possible to absorb torsional vibrations and bending vibrations, and further reduce abnormal noises such as muffled noise in the passenger compartment caused by these vibrations. [Structure] Input member 1 fixed to crankshaft 25 and converter housing 28 of torque converter 27
The output member 13 fixed to the above is assembled so as to be relatively rotatable by a predetermined angle, and the input member 1 and the output member 13 are elastically connected in the rotating direction by a plurality of spring members 16. The input member 1 is divided into a small diameter portion 2 and a large diameter portion 3, the small diameter portion 2 and the large diameter portion 3 are connected by a rubber-like elastic member 10, and the small diameter portion 2 and the large diameter portion 3 are connected. A stopper 12 for restricting relative rotation of the both is formed between the two.
Description
【０００１】[0001]
本考案はエンジンから自動変速機に動力を伝達するための装置に関する。 The present invention relates to a device for transmitting power from an engine to an automatic transmission.
【０００２】[0002]
近年、自動車に搭載される自動変速機は、エンジンから延びるクランクシャフ トとトルクコンバータのコンバータハウジングとをトーションダンパ等の動力伝 達装置で連結し、エンジン側のトルク変動に伴う衝撃力を動力伝達装置で吸収し て、エンジンからトルクコンバータに円滑にトルク伝達が行われるように工夫さ れている。その結果、流体伝動装置を介することなく直接トルク伝達する場合（ 直結クラッチ作動時）においても、エンジン側の動力が出力軸側へ円滑に伝達さ れる（実開昭６０−２８６５０号公報参照）。 In recent years, in automatic transmissions installed in automobiles, the crank shaft extending from the engine and the converter housing of the torque converter are connected by a power transmission device such as a torsion damper to transmit the impact force due to torque fluctuations on the engine side. It is devised so that it can be absorbed by the device and smoothly transmitted from the engine to the torque converter. As a result, even when the torque is directly transmitted without passing through the fluid transmission (when the direct coupling clutch is operated), the power on the engine side is smoothly transmitted to the output shaft side (see Japanese Utility Model Laid-Open No. 60-28650).
【０００３】[0003]
しかしながら、このような従来技術にあっては、クランクシャフトの捩り振動 及びそれに伴う振動音を低減化するのに優れた効果を発揮するものの、クランク シャフトの曲げ振動に起因する車室内のこもり音等の異音については未だ十分に 低減されていない。 However, although such a conventional technique has an excellent effect in reducing the torsional vibration of the crankshaft and the vibration noise associated therewith, the muffled noise in the vehicle interior due to the bending vibration of the crankshaft, etc. The abnormal noise is not sufficiently reduced.
【０００４】 そのため、クランクシャフトの捩り振動はもちろんのこと、曲げ振動をも効果 的に低減化することができる動力伝達装置の提供が望まれていた。Therefore, it has been desired to provide a power transmission device that can effectively reduce not only torsional vibration of the crankshaft but also bending vibration.
【０００５】 本考案はこのような要望に応えるために案出されたものである。The present invention has been devised to meet such a demand.
【０００６】[0006]
即ち本考案は、クランクシャフトに固定される入力部材とトルクコンバータの コンバータハウジングに固定される出力部材とを所定角度相対回動できるように 組み付け、これら入力部材と出力部材とを複数のばね部材で回動方向に弾性的に 連繋してなる自動変速機の動力伝達装置であって、前記入力部材を小径部と大径 部とに分割し、これ小径部と大径部とをゴム状弾性部材で連繋すると共に、小径 部と大径部との間に両者の相対回動を規制するストッパを形成したことを特徴と している。又、ストッパに小径部と大径部の相対回動を許容するクリアランスを 設けたことを特徴としている。 That is, according to the present invention, the input member fixed to the crankshaft and the output member fixed to the converter housing of the torque converter are assembled so as to be relatively rotatable by a predetermined angle, and these input member and output member are formed by a plurality of spring members. A power transmission device for an automatic transmission elastically linked in a rotating direction, wherein the input member is divided into a small diameter portion and a large diameter portion, and the small diameter portion and the large diameter portion are rubber-like elastic members. It is characterized in that a stopper is formed between the small-diameter portion and the large-diameter portion so as to restrict the relative rotation of the both. Further, it is characterized in that the stopper is provided with a clearance allowing relative rotation of the small diameter portion and the large diameter portion.
【０００７】[0007]
小径部と大径部の軸方向及び半径方向への相対移動が可能となり、クランクシ ャフトから伝達される曲げ振動がゴム状弾性部材で吸収される。 The small-diameter portion and the large-diameter portion can be relatively moved in the axial direction and the radial direction, and the bending vibration transmitted from the crankshaft is absorbed by the rubber-like elastic member.
【０００８】 一方、小径部と大径部は、ストッパで両者の相対回動が阻止されるため、クラ ンクシャフトとともに回動し、ばね部材を押し縮めて出力部材と相対回動する。 従って、クランクシャフトから伝達される捩り振動がばね部材で吸収される。On the other hand, the small-diameter portion and the large-diameter portion are prevented from rotating relative to each other by the stopper, so that they rotate together with the crankshaft and compress the spring member to rotate relative to the output member. Therefore, the torsional vibration transmitted from the crankshaft is absorbed by the spring member.
【０００９】 又、ストッパに小径部と大径部の相対回動を許容するクリアランスを設けた場 合には、捩り角度が小さな微小捩り振動が低剛性のゴム状弾性部材で吸収され、 捩り角度が大きな捩り振動がばね部材で吸収される。When the stopper is provided with a clearance allowing relative rotation of the small-diameter portion and the large-diameter portion, a small torsional vibration with a small torsion angle is absorbed by the rubber-like elastic member with low rigidity, and the torsion angle is reduced. The large torsional vibration is absorbed by the spring member.
【００１０】[0010]
以下本考案の実施例を図面に基づき詳述する。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
【００１１】 図１は本考案の一実施例を示す動力伝達装置Ａの断面図であり、図２は同正面 図である。これらの図において１は入力部材であり、この入力部材１は小径部２ と大径部３に分割してある。FIG. 1 is a sectional view of a power transmission device A showing an embodiment of the present invention, and FIG. 2 is a front view of the same. In these figures, 1 is an input member, and this input member 1 is divided into a small diameter portion 2 and a large diameter portion 3.
【００１２】 このうち小径部２は、略円板状のプレート部分２ａ及びこのプレート部分２ａ の外周端に形成した円筒部分２ｂとから成っている。そして、この小径部２のプ レート部分２ａにはボルト取付穴４を周方向に複数形成してあり、円筒部分２ｂ には周方向に複数の切り欠き溝５を形成してある。Of these, the small-diameter portion 2 is composed of a substantially disc-shaped plate portion 2a and a cylindrical portion 2b formed at the outer peripheral end of the plate portion 2a. A plurality of bolt mounting holes 4 are formed in the plate portion 2a of the small diameter portion 2 in the circumferential direction, and a plurality of cutout grooves 5 are formed in the cylindrical portion 2b in the circumferential direction.
【００１３】 一方、大径部３は、左右一対のドライブプレート６ａ，６ｂから成り、両者の 内周側を複数のリベット７で固定し、両者間に半径方向外方へ向かって開口する 環状空間８を形成してある。そして、この大径部３の一方のドライブプレート６ ａの内周側円筒部分９を小径部２の円筒部分２ｂにゴム状弾性部材１０で連繋し てある。尚、ゴム状弾性部材１０は、図２に示すように、両円筒部分２ｂ，９の 全周に亘り加硫接着しているが、これに限らず両円筒部分２ｂ，９の円周方向複 数箇所を部分的に連繋するようにしてもよい。On the other hand, the large-diameter portion 3 is composed of a pair of left and right drive plates 6a and 6b, the inner peripheral sides of which are fixed by a plurality of rivets 7, and an annular space which opens outward in the radial direction between the two. 8 is formed. The inner peripheral side cylindrical portion 9 of the one drive plate 6a of the large diameter portion 3 is connected to the cylindrical portion 2b of the small diameter portion 2 by a rubber-like elastic member 10. As shown in FIG. 2, the rubber-like elastic member 10 is vulcanized and adhered over the entire circumference of both the cylindrical portions 2b and 9; however, the present invention is not limited to this. You may make it connect several places partially.
【００１４】 又、大径部３の内周端には、小径部２の切り欠き溝５に係合する爪１１を複数 形成してある。そして、この爪１１と切り欠き溝５が小径部２と大径部３の相対 回動を阻止するストッパ１２を構成する。尚、このストッパ１２は、小径部２と 大径部３の軸方向（図１中左右方向）及び半径方向（図１中上下方向）への相対 移動を許容するように、爪１１と切り欠き溝５の間に所定のクリアランスＣ1， Ｃ2を設けてある（図４参照）。A plurality of claws 11 that engage with the cutout grooves 5 of the small diameter portion 2 are formed at the inner peripheral end of the large diameter portion 3. The claw 11 and the notch groove 5 constitute a stopper 12 that prevents the small diameter portion 2 and the large diameter portion 3 from rotating relative to each other. The stopper 12 is provided with a notch 11 and a notch so as to allow relative movement of the small diameter portion 2 and the large diameter portion 3 in the axial direction (left-right direction in FIG. 1) and the radial direction (vertical direction in FIG. 1). Predetermined clearances C 1 and C 2 are provided between the grooves 5 (see FIG. 4).
【００１５】 １３は略円筒状の出力部材であり、この出力部材１３は前記ドライブプレート ６ａ，６ｂ間の環状空間８内に収容してある。そして、この出力部材１３の外周 側には周方向に延びる長穴１４を複数形成してあり、この長穴１４には両ドライ ブプレート６ａ，６ｂの外周端部を固定するストップピン１５を係合し、このス トップピン１５と長穴１４とでドライブプレート６ａ，６ｂと出力部材１３の相 対回動量を規制するようにしてある。Reference numeral 13 denotes a substantially cylindrical output member, and the output member 13 is housed in the annular space 8 between the drive plates 6a and 6b. A plurality of elongated holes 14 extending in the circumferential direction are formed on the outer peripheral side of the output member 13, and a stop pin 15 for fixing the outer peripheral ends of both drive plates 6a and 6b is engaged with the elongated holes 14. The stop pin 15 and the elongated hole 14 regulate the relative rotation amount of the drive plates 6a and 6b and the output member 13.
【００１６】 １６はばね部材である。このばね部材１６は、ドライブプレート６ａ，６ｂ及 び出力部材１３の相対応する位置に複数形成した窓１７，１８，１９内に遊動子 ２０のアーム２０ａを介して一対収容してあり、ドライブプレート６ａ，６ｂと 出力部材１３とを回動方向に弾性的に連繋している。その結果、このばね部材１ ６は、ドライブプレート６ａ，６ｂと出力部材１３とが相対回動した際に、遊動 子２０のアーム２０ａを介して直列に作用し、回転変動に伴う衝撃を吸収する。 遊動子２０は、環状の基部２０ｂ及びこの基部２０ｂから半径方向外方へ突出す る複数のアーム２０ａとからなり、基部２０ｂを出力部材１３とドライブプレー ト６ｂとの間に相対回動できるように収容してある。Reference numeral 16 is a spring member. A pair of the spring members 16 are accommodated in a plurality of windows 17, 18 and 19 formed at corresponding positions of the drive plates 6a and 6b and the output member 13 via an arm 20a of the idler 20 to form a pair of drive plates. 6a and 6b and the output member 13 are elastically connected in the rotational direction. As a result, when the drive plates 6a, 6b and the output member 13 rotate relative to each other, the spring member 16 acts in series via the arm 20a of the idler 20 and absorbs the shock caused by the rotation fluctuation. . The idler 20 includes an annular base portion 20b and a plurality of arms 20a protruding radially outward from the base portion 20b. The base portion 20b can be relatively rotated between the output member 13 and the drive plate 6b. It is housed in.
【００１７】 尚、ドライブプレート６ａ，６ｂの外周側には周方向に長い穴２１を複数形成 してあり、出力部材１３の外周側にはボルト穴２２を前記穴２１と同数形成して ある。又、ドライブプレート６ａの外周側円筒部分２３には、図外のスタータモ ータのピニオンギヤに噛合するリングギヤ２４を溶接してある。A plurality of holes 21 that are long in the circumferential direction are formed on the outer peripheral sides of the drive plates 6 a and 6 b, and the same number of bolt holes 22 as the holes 21 are formed on the outer peripheral side of the output member 13. A ring gear 24 that meshes with a pinion gear of a starter motor (not shown) is welded to the outer peripheral cylindrical portion 23 of the drive plate 6a.
【００１８】 図３は以上のように構成した動力伝達装置Ａの取付状態を示す図であり、この 図に示すように入力部材１の小径部２は、そのプレート部分２ａをクランクシャ フト２５にボルト２６で固定してある。一方、大径部３のドライブプレート６ｂ は、その穴２１をトルクコンバータ２７のコンバータハウジング２８の取付部２ ９に係合してある。そして、出力部材１３のボルト穴２２に係合したボルト３０ により出力部材１３をコンバータハウジング２８に固定してある。FIG. 3 is a diagram showing a mounting state of the power transmission device A configured as described above. As shown in FIG. 3, the small diameter portion 2 of the input member 1 has its plate portion 2a mounted on the crank shaft 25. It is fixed with bolts 26. On the other hand, the drive plate 6b of the large diameter portion 3 has its hole 21 engaged with the mounting portion 29 of the converter housing 28 of the torque converter 27. Then, the output member 13 is fixed to the converter housing 28 by the bolts 30 engaged with the bolt holes 22 of the output member 13.
【００１９】 尚、この図３において３１は出力軸３２にスプライン嵌合させたタービンハブ であり、このタービンハブ３１のフランジ部３１ａにはタービン・ランナ３３を 固定し、ボス部３１ｂには直結クラッチ（ピストン）３４をスライドできるよう に嵌合してある。直結クラッチ３４は、その背面に形成した複数の爪３５をター ビンハブ３１の外周端に形成した溝３６に係合してあるため、タービンハブ３１ とともに回動する。そして、この直結クラッチ３４は、車両速度が所定速度以上 となり、直結クラッチ３４の背面側の油圧力Ｐ1が直結クラッチ３４の正面側の 油圧力Ｐ2よりも大きくなると、図３中左側方向へスライドしてコンバータハウ ジング２８の内側壁２８ａに接合する（ロックアップする）。In FIG. 3, reference numeral 31 denotes a turbine hub spline-fitted to the output shaft 32. A turbine runner 33 is fixed to the flange portion 31a of the turbine hub 31, and a direct coupling clutch is attached to the boss portion 31b. The (piston) 34 is fitted so that it can slide. The direct coupling clutch 34 rotates with the turbine hub 31 because the plurality of pawls 35 formed on the back surface thereof are engaged with the grooves 36 formed on the outer peripheral end of the turbine hub 31. When the vehicle speed of the direct coupling clutch 34 becomes higher than a predetermined speed and the hydraulic pressure P 1 on the back side of the direct coupling clutch 34 becomes larger than the hydraulic pressure P 2 on the front side of the direct coupling clutch 34, the direct coupling clutch 34 moves to the left side in FIG. It is slid and joined (locked up) to the inner wall 28a of the converter housing 28.
【００２０】 このような本実施例構造によれば、出力部材１３の小径部２と大径部３は、ス トッパ１２により相対回動が阻止されるようになっているが、図１中上下方向及 び左右方向にはゴム状弾性部材１０で支持され、両者の相対移動が許容される。 その結果、動力伝達装置Ａの曲げ剛性が小さくなり、クランクシャフト系の固有 曲げ振動数を変化させることができ、エンジン（図示せず）の常用回転域におけ るクランクシャフト系の曲げ振動を吸収することができ、曲げ振動に起因する車 室内のこもり音等の異音を低減化することができる。According to the structure of this embodiment, the small diameter portion 2 and the large diameter portion 3 of the output member 13 are prevented from rotating relative to each other by the stopper 12. The rubber-like elastic member 10 is supported in the left-right direction and the left-right direction, and relative movement of the both is allowed. As a result, the flexural rigidity of the power transmission device A is reduced, the natural bending frequency of the crankshaft system can be changed, and the bending vibration of the crankshaft system in the normal rotation range of the engine (not shown) is absorbed. Therefore, it is possible to reduce abnormal noise such as muffled noise in the vehicle interior due to bending vibration.
【００２１】 又、本実施例は、クランクシャフト２５及びコンバータハウジング２８と動力 伝達装置Ａとの間に組み付け誤差を生じても、入力部材１の小径部２と大径部３ とを連繋するゴム状弾性部材１０が変形するため、その組み付け誤差を吸収する ことができる。Further, in the present embodiment, even if an assembly error occurs between the crankshaft 25 and the converter housing 28 and the power transmission device A, a rubber that connects the small diameter portion 2 and the large diameter portion 3 of the input member 1 to each other. Since the elastic member 10 is deformed, the assembly error can be absorbed.
【００２２】 尚、本実施例構造によれば、入力部材１の小径部２と大径部３はストッパ１２ によりその相対回動が阻止されるようになっているため、クランクシャフト２５ の回転変動に伴う衝撃はドライブプレート６ａ，６ｂと出力部材１３を連繋する ばね部材１６により吸収され、クランクシャフト２５の捩り振動及びそれに伴う 振動音が低減化される。その結果、エンジンの回動力は、クランクシャフト２５ ，動力伝達装置Ａ及びトルクコンバータ２７を介して出力軸３２に円滑に伝達さ れる。According to the structure of the present embodiment, since the relative rotation of the small diameter portion 2 and the large diameter portion 3 of the input member 1 is blocked by the stopper 12, the rotation fluctuation of the crankshaft 25. Is absorbed by the spring member 16 that connects the drive plates 6a and 6b to the output member 13, and the torsional vibration of the crankshaft 25 and the accompanying vibration noise are reduced. As a result, the rotational power of the engine is smoothly transmitted to the output shaft 32 via the crankshaft 25, the power transmission device A and the torque converter 27.
【００２３】 図５は本考案の他の実施例を示したものであり、入力部材１の小径部２と大径 部３との連繋状態を示す断面図である。この図に示すように、小径部２を２枚の プレート部材３７，３８で構成し、一方のプレート部材３７の外周端の周方向に 複数形成した切り欠き溝３９に一方のドライブプレート６ａの爪４０を係合させ ると共に、他方のプレート部材３８の円筒部分３８ａの周方向に複数形成した切 り欠き溝４１に他方のドライブプレート６ｂの爪４２を係合させてある。そして 、一方のプレート部材３７の側面と他方のドライブプレート６ｂの側面とをゴム 状弾性部材１０で連繋している。尚、切り欠き溝３９，４１及び爪４０，４２で ストッパ１２を構成している。又、一方のプレート部材３７の外周端と一方のド ライブプレート６ａの内周端とが干渉しないように所定のクリアランスＣ3を設 けてある。本実施例によっても前記実施例と同様の効果を得ることができる。FIG. 5 shows another embodiment of the present invention, and is a sectional view showing a state in which the small diameter portion 2 and the large diameter portion 3 of the input member 1 are connected. As shown in this figure, the small-diameter portion 2 is composed of two plate members 37 and 38, and a plurality of notch grooves 39 formed in the circumferential direction of the outer peripheral end of one plate member 37 are provided with claws of one drive plate 6a. 40 is engaged, and the claws 42 of the other drive plate 6b are engaged with the notch grooves 41 formed in the circumferential direction of the cylindrical portion 38a of the other plate member 38. The rubber-like elastic member 10 connects the side surface of one plate member 37 and the side surface of the other drive plate 6b. The cutout grooves 39, 41 and the claws 40, 42 constitute the stopper 12. Further, a predetermined clearance C 3 is provided so that the outer peripheral end of the one plate member 37 and the inner peripheral end of the one drive plate 6a do not interfere with each other. According to this embodiment, the same effect as that of the above embodiment can be obtained.
【００２４】 図６は本考案の更に他の実施例を示すものであり、入力部材１の小径部２と大 径部３との連繋状態を示す断面図である。この図に示すように、小径部２の円筒 部分２ｂには半球状の溝４３を周方向に複数形成し、この溝４３内に鋼球４４を 収容してある。そして、大径部３の内周端に複数形成した半球状の溝４５を前記 鋼球４４に係合してある。そして、大径部３を構成する両ドライブプレート６ａ ，６ｂと小径部２の円筒部分２ｂとをゴム状弾性部材１０，１０で連繋してある 。尚、溝４３，４５及び鋼球４４とでストッパ１２を構成してあり、鋼球４４と 各半球状の溝４３，４５との間及び小径部２の円筒部分２ｂと大径部３の内周端 との間には所定のクリアランスＣ4，Ｃ5を設けてある。従って、小径部２と大径 部３は、そのクリアランス量に応じて図６中上下方向及び左右方向への相対移動 が許容され、さらに相対回動をも許容される。FIG. 6 shows still another embodiment of the present invention, and is a sectional view showing a state in which the small diameter portion 2 and the large diameter portion 3 of the input member 1 are connected. As shown in this figure, a plurality of hemispherical grooves 43 are formed in the cylindrical portion 2b of the small diameter portion 2 in the circumferential direction, and steel balls 44 are housed in the grooves 43. A plurality of hemispherical grooves 45 formed at the inner peripheral end of the large diameter portion 3 are engaged with the steel balls 44. The drive plates 6a and 6b forming the large diameter portion 3 and the cylindrical portion 2b of the small diameter portion 2 are connected by the rubber-like elastic members 10 and 10. In addition, the stoppers 12 are constituted by the grooves 43, 45 and the steel balls 44, and between the steel balls 44 and the respective hemispherical grooves 43, 45 and between the cylindrical portion 2b of the small diameter portion 2 and the large diameter portion 3. Predetermined clearances C 4 and C 5 are provided between the peripheral edge and the peripheral edge. Therefore, the small diameter portion 2 and the large diameter portion 3 are allowed to move relative to each other in the vertical direction and the horizontal direction in FIG.
【００２５】 このように構成された本実施例によれば、前記実施例と同様に曲げ振動を低減 化できることはもちろんのこと、捩り角度が小さな微小捩り振動に対しては低剛 性のゴム状弾性部材１０のみを作用させる一方、捩り角度が大きな捩り振動に対 してはばね部材１６を作用させることにより、より一層効果的に捩り振動を低減 化することができる。According to the present embodiment configured as described above, it is of course possible to reduce bending vibration as in the case of the above-mentioned embodiment, and a rubber-like material having a low rigidity with respect to small torsional vibration with a small torsion angle. By acting only the elastic member 10 and acting the spring member 16 against the torsional vibration having a large torsion angle, the torsional vibration can be more effectively reduced.
【００２６】 尚、図１〜図５に示した実施例においても、ストッパ１２に周方向のクリアラ ンスを設ければ本実施例と同様の効果が得られる。又、これら各実施例において 、ゴム状弾性部材１０の材料，形状及び接着部位を適宜変更すれば、使用条件に 適合する曲げ剛性にすることができる。In the embodiment shown in FIGS. 1 to 5, if the stopper 12 is provided with a clearance in the circumferential direction, the same effect as that of this embodiment can be obtained. Further, in each of these embodiments, by appropriately changing the material, shape, and bonding portion of the rubber-like elastic member 10, it is possible to make the bending rigidity suitable for the usage conditions.
【００２７】[0027]
以上の説明から明らかなように本考案は、クランクシャフトに固定される入力 部材を小径部と大径部とに分割し、これら小径部と大径部とをゴム状弾性部材で 連繋すると共に、小径部と大径部との間に両者の相対回動を阻止するストッパを 形成してあるため、捩り振動は入力部材と出力部材とを回動方向に弾性的に連繋 するばね部材で吸収し、曲げ振動はゴム状弾性部材で吸収することができ、これ ら振動に起因する車室内のこもり音等の異音をより一層効果的に低減化すること ができる。 As is clear from the above description, the present invention divides the input member fixed to the crankshaft into a small diameter portion and a large diameter portion, and connects the small diameter portion and the large diameter portion with a rubber-like elastic member, and Since a stopper is formed between the small diameter portion and the large diameter portion to prevent relative rotation of the two, torsional vibration is absorbed by a spring member that elastically connects the input member and the output member in the rotation direction. The bending vibration can be absorbed by the rubber-like elastic member, and thus the abnormal noise such as the muffled noise in the vehicle interior caused by the vibration can be further effectively reduced.
【００２８】 又、ストッパに小径部と大径部の相対回動を許容するクリアランスを設けるこ とにより、捩り角度が小さな微小捩り振動はゴム状弾性部材で吸収することがで き、捩り角度が大きな捩り振動はばね部材で吸収することができるため、捩り振 動を広範囲に亘り効果的に低減化することができる。By providing the stopper with a clearance allowing relative rotation of the small-diameter portion and the large-diameter portion, a small torsional vibration with a small torsion angle can be absorbed by the rubber-like elastic member, and the torsion angle can be reduced. Since a large torsional vibration can be absorbed by the spring member, the torsional vibration can be effectively reduced over a wide range.
【図面の簡単な説明】[Brief description of drawings]
【図１】本考案の一実施例を示す動力伝達装置の断面図
（図２のＢ−Ｂ線に沿う断面図）。FIG. 1 is a cross-sectional view of a power transmission device according to an embodiment of the present invention (a cross-sectional view taken along the line BB of FIG. 2).
【図２】一部を切り欠いて示す動力伝達装置の断面図。FIG. 2 is a cross-sectional view of the power transmission device with a part cut away.
【図３】動力伝達装置の取付状態を示す断面図。FIG. 3 is a cross-sectional view showing a mounted state of the power transmission device.
【図４】動力伝達装置の要部拡大断面図。FIG. 4 is an enlarged cross-sectional view of a main part of the power transmission device.
【図５】本考案の他の実施例を示す動力伝達装置の要部
拡大断面図。FIG. 5 is an enlarged sectional view of an essential part of a power transmission device showing another embodiment of the present invention.
【図６】本考案の更に他の実施例を示す動力伝達装置の
要部拡大断面図。FIG. 6 is an enlarged sectional view of a main part of a power transmission device showing still another embodiment of the present invention.
Ａ…動力伝達装置、１…入力部材、２…小径部、３…大
径部、１０…ゴム状弾性部材、１２…ストッパ、１３…
出力部材、１６…ばね部材、２５…クランクシャフト、
２７…トルクコンバータ、２８…コンバータハウジン
グ、Ｃ4…クリアランス。A ... Power transmission device, 1 ... Input member, 2 ... Small diameter part, 3 ... Large diameter part, 10 ... Rubber-like elastic member, 12 ... Stopper, 13 ...
Output member, 16 ... Spring member, 25 ... Crank shaft,
27 ... torque converter, 28 ... converter housing, C 4 ... clearance.
Claims (2)
とトルクコンバータのコンバータハウジングに固定され
る出力部材とを所定角度相対回動できるように組み付
け、これら入力部材と出力部材とを複数のばね部材で回
動方向に弾性的に連繋してなる自動変速機の動力伝達装
置において、前記入力部材を小径部と大径部とに分割
し、これら小径部と大径部とをゴム状弾性部材で連繋す
ると共に、小径部と大径部との間に両者の相対回動を阻
止するストッパを形成したことを特徴とする自動変速機
の動力伝達装置。1. An input member fixed to a crankshaft and an output member fixed to a converter housing of a torque converter are assembled so as to be relatively rotatable at a predetermined angle, and these input member and output member are formed by a plurality of spring members. In a power transmission device of an automatic transmission elastically connected in a rotating direction, the input member is divided into a small diameter portion and a large diameter portion, and the small diameter portion and the large diameter portion are connected by a rubber-like elastic member. In addition, a power transmission device for an automatic transmission characterized in that a stopper is formed between the small diameter portion and the large diameter portion so as to prevent relative rotation of the both.
置において、ストッパに小径部と大径部の相対回動を許
容するクリアランスを設けたことを特徴とする自動変速
機の動力伝達装置。2. The power transmission device for an automatic transmission according to claim 1, wherein the stopper is provided with a clearance allowing relative rotation of the small diameter portion and the large diameter portion. ..
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991088659U JP2585099Y2 (en) | 1991-10-29 | 1991-10-29 | Power transmission for automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991088659U JP2585099Y2 (en) | 1991-10-29 | 1991-10-29 | Power transmission for automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0540644U true JPH0540644U (en) | 1993-06-01 |
| JP2585099Y2 JP2585099Y2 (en) | 1998-11-11 |
Family
ID=13948953
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1991088659U Expired - Fee Related JP2585099Y2 (en) | 1991-10-29 | 1991-10-29 | Power transmission for automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2585099Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000002313A (en) * | 1998-06-16 | 2000-01-07 | Unisia Jecs Corp | Torsion damper |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5879156U (en) * | 1981-11-25 | 1983-05-28 | 日産自動車株式会社 | Torque converter torsional damper |
| JPH0243931A (en) * | 1988-08-02 | 1990-02-14 | Mitsubishi Heavy Ind Ltd | Apparatus for making carbonated beverage |
-
1991
- 1991-10-29 JP JP1991088659U patent/JP2585099Y2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5879156U (en) * | 1981-11-25 | 1983-05-28 | 日産自動車株式会社 | Torque converter torsional damper |
| JPH0243931A (en) * | 1988-08-02 | 1990-02-14 | Mitsubishi Heavy Ind Ltd | Apparatus for making carbonated beverage |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000002313A (en) * | 1998-06-16 | 2000-01-07 | Unisia Jecs Corp | Torsion damper |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2585099Y2 (en) | 1998-11-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9841060B2 (en) | Torsional vibration damper for hydrokinetic torque coupling device with inner and outer elastic damping members connected in series | |
| US5203835A (en) | Lock-up torque converter for automatic transmission | |
| US20150362041A1 (en) | Torsional vibration damper for hydrokinetic torque coupling device | |
| JPH0518440A (en) | Rotational variation absorbing device | |
| JP2018531351A6 (en) | Torsional vibration damper for hydrodynamic torque coupling device with inner and outer elastic damping members connected in series | |
| JP3680093B2 (en) | Automotive flywheel and double mass flywheel | |
| US6119549A (en) | Flywheel assembly and a torque converter | |
| US6899210B2 (en) | Piston coupling mechanism and lockup device for fluid-type torque transmission device equipped with the same | |
| JPH04211744A (en) | Automobile power transmission device | |
| JP2008215593A (en) | Hydraulic torque transmission device | |
| US7222706B2 (en) | Lockup device for hydraulic torque transmission device | |
| US10047845B2 (en) | Dynamic absorber for torsional vibration damper of hydrokinetic torque coupling device | |
| US10054208B2 (en) | Frequency dynamic absorber for torsional vibration damper of hydrokinetic torque coupling device | |
| KR20220101563A (en) | Vibration dampers for vehicles and vehicles | |
| EP0238235A2 (en) | Torsion damping mechanism | |
| JPH0550202U (en) | Power transmission device | |
| JPH0540644U (en) | Power transmission device for automatic transmission | |
| US10428926B2 (en) | Hydrokinetic torque coupling device with turbine made of lightweight material and torsional vibration damper | |
| US10006531B2 (en) | Lock-up clutch and torsional vibration damper for hydrokinetic torque coupling device, and related methods | |
| JP3474624B2 (en) | Damper device | |
| JP2582854Y2 (en) | Power transmission for automatic transmission | |
| JPH05288239A (en) | Power transmission device for automatic transmission | |
| JP3474625B2 (en) | Damper device | |
| JPH0550164U (en) | Power transmission device | |
| JPH0714253U (en) | Automatic transmission power transmission device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R323117 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| LAPS | Cancellation because of no payment of annual fees |