JP2006258265A - Fluid transmission device - Google Patents

Fluid transmission device Download PDF

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Publication number
JP2006258265A
JP2006258265A JP2005080200A JP2005080200A JP2006258265A JP 2006258265 A JP2006258265 A JP 2006258265A JP 2005080200 A JP2005080200 A JP 2005080200A JP 2005080200 A JP2005080200 A JP 2005080200A JP 2006258265 A JP2006258265 A JP 2006258265A
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transmission device
annular
transmission cover
fluid transmission
cover
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JP4537871B2 (en
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Yoshihisa Yamamoto
芳久 山本
Akira Kitajima
晃 北嶋
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Yutaka Giken Co Ltd
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Yutaka Giken Co Ltd
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Priority to JP2005080200A priority Critical patent/JP4537871B2/en
Priority to US11/157,158 priority patent/US7284645B2/en
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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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H2041/243—Connections between pump shell and cover shell of the turbine

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Abstract

<P>PROBLEM TO BE SOLVED: To realize improvement of durability by relaxing excessive stress concentration at a corner welded part between a pump shell and a transmission cover coupled with large size of the pump shell and the transmission cover. <P>SOLUTION: In the fluid transmission device, a male fitting surface 45 of an outer periphery of a diameter enlargement part 2sa of the pump shell 2s and a female fitting surface 47 of an inner periphery of a peripheral wall part 5a of the cylindrical transmission cover 5 are fitted to each other and the pump shell 2s and the transmission cover 5 are bonded to each other by forming the corner welded part 52 between an end surface of the peripheral wall part 5a and an outer peripheral surface of the diameter enlargement part 2sa. An annular recessed part 48 adjacent to the female fitting surface 47 at an opposite side to the corner welded part 52 is formed on the inner peripheral surface of the peripheral wall part 5a and a part of the transmission cover 5 corresponding to the recessed part 48 is made to an annular thin thickness part 49. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は，自動車等に使用されるトルクコンバータや流体継手を含む流体伝動装置に関し，特に，タービン羽根車に対置されて，それとの間に作動オイルの循環回路を画成するポンプ羽根車のポンプシェルの外周側端部に拡径部を延設し，この拡径部外周の雄嵌合面と，タービン羽根車の背面との間に循環回路に連通する油室を画成する円筒状の伝動カバーの周壁部内周の雌嵌合面とを相互に嵌合し，前記周壁部の端面と前記拡径部の外周面との間に全周に亙る隅肉溶接部を形成することにより，ポンプシェル及び伝動カバーを相互に結合した流体伝動装置の改良に関する。   The present invention relates to a fluid transmission device including a torque converter and a fluid coupling used in automobiles and the like, and in particular, a pump impeller pump which is opposed to a turbine impeller and defines a circulation circuit for hydraulic oil therebetween. An expanded diameter portion is extended at the outer peripheral end of the shell, and a cylindrical oil chamber defining an oil chamber communicating with the circulation circuit is provided between the male fitting surface of the expanded diameter outer periphery and the rear surface of the turbine impeller. By fitting a female fitting surface on the inner periphery of the peripheral wall portion of the transmission cover to each other, and forming a fillet welded portion extending over the entire circumference between the end surface of the peripheral wall portion and the outer peripheral surface of the enlarged diameter portion, The present invention relates to an improvement of a fluid transmission device in which a pump shell and a transmission cover are coupled to each other.

かゝる流体伝動装置は，例えば下記特許文献１に開示されているように，既に知られている。
特開２００４−２３９３６５号公報 Such a fluid transmission device is already known as disclosed in, for example, Patent Document 1 below.
JP 2004-239365 A

近年，かゝる流体伝動装置では，エンジンの高出力化に伴ない負荷容量の増加が要求され，それに対応してポンプシェル及び伝動カバーからなる流体容器の大径化が必要となる。しかしながら，上記流体容器が大径化すると，遠心力及び内部圧力の増加により，その周壁に作用する半径方向の荷重が大幅に増大するため，ポンプシェル及び伝動カバー間の溶接部に過大な応力が集中し易くなる。そこで，ポンプシェル及び伝動カバーの板厚を増し，それらの剛性を高めて，溶接部の応力を軽減することができるが考えられるが，そのようにすれば流体容器の重量が大幅に増加し，コスト高を招くのみならず，加速応答性等の性能の低下を来すことになる。   In recent years, in such a fluid transmission device, an increase in load capacity is required as the engine output increases, and accordingly, the diameter of a fluid container including a pump shell and a transmission cover needs to be increased. However, when the diameter of the fluid container is increased, the radial load acting on the peripheral wall is greatly increased due to an increase in centrifugal force and internal pressure, so that excessive stress is applied to the weld between the pump shell and the transmission cover. It becomes easy to concentrate. Therefore, it is conceivable that the thickness of the pump shell and transmission cover can be increased to increase their rigidity and reduce the stress at the weld. However, if this is done, the weight of the fluid container will increase significantly, Not only will the cost be increased, but performance such as acceleration response will be degraded.

本発明は，かゝる事情に鑑みてなされたもので，ポンプシェル及び伝動カバーからなる流体容器の大径化によるも，それらの板厚を特に増すことなく，ポンプシェル及び伝動カバー間の溶接部での過大な応力集中を緩和して，その耐久性の向上を図ることができるようにした前記流体伝動装置を提供することを目的とする。   The present invention has been made in view of such circumstances, and even if the diameter of the fluid container including the pump shell and the transmission cover is increased, the weld between the pump shell and the transmission cover is not particularly increased without increasing the plate thickness thereof. It is an object of the present invention to provide the fluid transmission device that can relieve excessive stress concentration in the section and improve its durability.

上記目的を達成するために，本発明は，タービン羽根車に対置されて，それとの間に作動オイルの循環回路を画成するポンプ羽根車のポンプシェルの外周側端部に拡径部を延設し，この拡径部外周の雄嵌合面と，タービン羽根車の背面との間に循環回路に連通する油室を画成する円筒状の伝動カバーの周壁部内周の雌嵌合面とを相互に嵌合し，前記周壁部の端面と前記拡径部の外周面との間に全周に亙る隅肉溶接部を形成することにより，ポンプシェル及び伝動カバーを相互に結合した流体伝動装置において，前記周壁部の内周面に，前記隅肉溶接部と反対側で前記雌嵌合面と隣接する環状の凹部を形成して，この凹部に対応する伝動カバーの部分を，その両側の部分より肉厚が薄い環状薄肉部となしたことを第１の特徴とする。   In order to achieve the above object, the present invention extends a diameter-expanded portion to an outer peripheral side end of a pump shell of a pump impeller that is opposed to a turbine impeller and defines a working oil circulation circuit therebetween. And a female mating surface on the inner circumference of the cylindrical transmission cover that defines an oil chamber communicating with the circulation circuit between the male mating surface on the outer periphery of the enlarged diameter portion and the rear surface of the turbine impeller. Are connected to each other, and a fillet welded portion extending over the entire circumference is formed between the end surface of the peripheral wall portion and the outer peripheral surface of the enlarged-diameter portion, thereby connecting the pump shell and the transmission cover to each other. In the device, an annular recess is formed on the inner peripheral surface of the peripheral wall portion on the side opposite to the fillet welded portion and adjacent to the female fitting surface, and portions of the transmission cover corresponding to the recess are disposed on both sides thereof. The first characteristic is that the annular thin portion is thinner than the portion.

また本発明は，第１の特徴に加えて，前記拡径部の端部に，前記凹部を内周側から覆って該凹部を袋状の異物溜まりにする環状の覆い壁を延設し，この覆い壁の先端側で前記異物溜まりを前記油室に連通したことを第２の特徴とする。   In addition to the first feature of the present invention, an annular covering wall is provided at the end of the enlarged diameter portion so as to cover the concave portion from the inner peripheral side and make the concave portion a bag-like foreign substance reservoir. A second feature is that the foreign substance reservoir communicates with the oil chamber at the front end side of the covering wall.

また本発明は，第１又は第２の特徴に加えて，前記凹部の両内側面と底面とを，連続した曲面で構成したことを第３の特徴とする。   Moreover, in addition to the 1st or 2nd characteristic, this invention makes it the 3rd characteristic that the both inner surface and bottom face of the said recessed part were comprised by the continuous curved surface.

さらに本発明は，第１〜第３の何れかに特徴に加えて，前記覆い壁の外周面に，前記凹部に臨む環状の肉抜き部を形成したことを第３の特徴とする。   Furthermore, the present invention is characterized in that, in addition to any of the first to third features, an annular lightening portion that faces the concave portion is formed on the outer peripheral surface of the covering wall.

さらにまた本発明は，第１〜第４の特徴の何れかに加えて，前記周壁部の外周面の，前記環状薄肉部と伝動カバーの側壁部との間にリングギヤを嵌合して溶接したことを第４の特徴とする。   Furthermore, in addition to any one of the first to fourth features, the present invention is configured such that a ring gear is fitted and welded between the annular thin portion and the side wall portion of the transmission cover on the outer peripheral surface of the peripheral wall portion. This is the fourth feature.

尚，前記流体伝動装置は，後述する本発明の実施例中のトルクコンバータＴに対応する。   The fluid transmission device corresponds to a torque converter T in an embodiment of the present invention described later.

本発明の第１の特徴によれば，伝動カバーの周壁部の内周面に，隅肉溶接部と反対側で雌嵌合面と隣接する環状の凹部を形成して，この凹部に対応する伝動カバーの部分を，その両側の部分より肉厚が薄い環状薄肉部となしたので，ポンプシェル及び伝動カバーに，遠心力及び内部圧力による半径方向の大なる荷重が加わっても，前記環状薄肉部が適度に撓むことにより，隅肉溶接部から環状薄肉部に応力が分散することになり，隅肉溶接部での過大応力の集中を効果的に緩和することができ，ポンプシェル及び伝動カバーの板厚を増すことなく，その耐久性の向上を図ることができる。   According to the first feature of the present invention, an annular recess is formed on the inner peripheral surface of the peripheral wall portion of the transmission cover on the side opposite to the fillet welded portion and adjacent to the female fitting surface. The transmission cover part is an annular thin part that is thinner than the parts on both sides. Therefore, even if a large radial load due to centrifugal force and internal pressure is applied to the pump shell and transmission cover, By appropriately bending the part, stress is distributed from the fillet weld to the annular thin part, and the concentration of excessive stress at the fillet weld can be effectively mitigated. The durability can be improved without increasing the thickness of the cover.

しかも環状薄肉部に隣接する雌嵌合面では周壁部の肉厚の減少はないから，隅肉溶接部の溶接代を充分に確保し得て，隅肉溶接部の強度を高めることができる。   In addition, since the wall thickness of the peripheral wall portion does not decrease on the female fitting surface adjacent to the annular thin wall portion, a sufficient welding allowance can be secured for the fillet welded portion, and the strength of the fillet welded portion can be increased.

また本発明の第２の特徴によれば，ポンプシェルの拡径部の端部には，前記凹部を内周側から覆って該凹部を袋状の異物溜まりにする環状の覆い壁を延設し，この覆い壁の先端側で前記異物溜まりを前記油室に連通したので，前記凹部を異物溜まりに利用して，流体伝動装置の作動中，作動オイルから遠心分離された異物を捕捉することができる。   According to the second feature of the present invention, an annular covering wall is provided at the end of the expanded diameter portion of the pump shell so as to cover the recess from the inner peripheral side and make the recess a bag-like foreign substance reservoir. In addition, since the foreign substance reservoir communicates with the oil chamber at the front end side of the covering wall, the concave portion is used as a foreign substance reservoir to capture the foreign substance centrifugally separated from the working oil during the operation of the fluid transmission device. Can do.

さらに本発明の第３の特徴によれば，前記凹部の両内側面と底面とを，連続した曲面で構成したので，前記環状薄肉部全体に応力を分散させて，該薄肉部の強度低下を防ぐことができる。   Further, according to the third feature of the present invention, since both the inner side surface and the bottom surface of the concave portion are formed by continuous curved surfaces, the stress is distributed over the entire annular thin portion, thereby reducing the strength of the thin portion. Can be prevented.

さらにまた本発明の第４の特徴によれば，前記覆い壁の外周面に，前記凹部に臨む環状の肉抜き部を形成したので，前記異物溜まりの容積を増加させることができる。   Furthermore, according to the fourth feature of the present invention, since the annular hollow portion facing the recess is formed on the outer peripheral surface of the covering wall, the volume of the foreign substance reservoir can be increased.

さらにまた本発明の第５の特徴によれば，伝動カバーの周壁部の外周面の，前記環状薄肉部と伝動カバーの側壁部との間にリングギヤを嵌合して溶接したので，前記周壁部をリングギヤの取り付け部に利用し得ると共に，リングギヤの溶接による環状薄肉部の熱歪を防ぐことができる。   Furthermore, according to the fifth feature of the present invention, since the ring gear is fitted and welded between the annular thin wall portion and the side wall portion of the transmission cover on the outer peripheral surface of the peripheral wall portion of the transmission cover, the peripheral wall portion Can be used for the ring gear mounting portion, and thermal deformation of the annular thin portion due to the ring gear welding can be prevented.

本発明の実施の形態を，添付図面に示す本発明の好適な実施例に基づいて以下に説明する。   Embodiments of the present invention will be described below on the basis of preferred embodiments of the present invention shown in the accompanying drawings.

図１は本発明の実施例に係る自動車用トルクコンバータの上半部縦断側面図，図２は図１の２部拡大図である。   FIG. 1 is a longitudinal sectional side view of an upper half of an automotive torque converter according to an embodiment of the present invention, and FIG. 2 is an enlarged view of part 2 of FIG.

図１において，自動車用のトルクコンバータＴは，ポンプ羽根車２と，それと対置されるタービン羽根車３と，それらの内周部間に配置されるステータ羽根車４とを備え，これら羽根車２，３，４間には作動オイルによる動力伝達のための循環回路６が画成される。ポンプ羽根車２のシェル，即ちポンプシェル２ｓには，タービン羽根車３の外側面を覆う伝動カバー５が次のように結合される。   In FIG. 1, a torque converter T for an automobile includes a pump impeller 2, a turbine impeller 3 opposed to the pump impeller 2, and a stator impeller 4 disposed between the inner peripheral portions thereof. , 3 and 4, a circulation circuit 6 for power transmission by hydraulic oil is defined. A transmission cover 5 that covers the outer surface of the turbine impeller 3 is coupled to the shell of the pump impeller 2, that is, the pump shell 2 s as follows.

図２に明示するように，ポンプシェル２ｓは，その外周端から半径方向外方に延びてタービン羽根車３の外周面を覆う円筒状の拡径部２ｓａを一体に有しており，この拡径部２ｓａの外周には，雄嵌合面４５と，この雄嵌合面４５の内端から立ち上がる環状の位置決め段部４６とが形成される。一方，伝動カバー５はポンプシェル２ｓより板厚が厚くなっており，上記拡径部２ｓａ側に開口する円筒状の周壁部５ａを有する。この周壁部５ａの内周には，その外端に連なる雌嵌合面４７と，この雌嵌合面４７の内端に隣接する環状の凹部４８とが形成され，周壁部５ａの，この凹部４８に対応する部分は，肉厚が凹部４８の両側部分のよりも薄い環状薄肉部４９となる。上記凹部４８の両側面及び底面は連続した曲面で構成されている。   As clearly shown in FIG. 2, the pump shell 2 s integrally has a cylindrical diameter-enlarged portion 2 sa that extends radially outward from the outer peripheral end and covers the outer peripheral surface of the turbine impeller 3. A male fitting surface 45 and an annular positioning step 46 rising from the inner end of the male fitting surface 45 are formed on the outer periphery of the diameter portion 2sa. On the other hand, the transmission cover 5 is thicker than the pump shell 2s and has a cylindrical peripheral wall portion 5a that opens to the enlarged diameter portion 2sa side. On the inner periphery of the peripheral wall portion 5a, a female fitting surface 47 connected to the outer end thereof and an annular concave portion 48 adjacent to the inner end of the female fitting surface 47 are formed, and this concave portion of the peripheral wall portion 5a is formed. A portion corresponding to 48 becomes an annular thin portion 49 whose thickness is thinner than both side portions of the recess 48. Both side surfaces and the bottom surface of the recess 48 are formed by continuous curved surfaces.

而して，ポンプシェル２ｓ及び伝動カバー５の結合に際しては，ポンプシェル２ｓの拡径部２ｓａの雄嵌合面４５と，伝動カバー５の周壁部５ａの雌嵌合面４７とを相互に嵌合して，拡径部２ｓａの位置決め段部４６に周壁部５ａの先端面を当接させる。しかる後，周壁部５ａの先端面と拡径部２ｓａの外周面と間に全周に亙る隅肉溶接部５２を形成する。こうしてポンプシェル２ｓ及び伝動カバー５は相互に結合される。   Thus, when the pump shell 2s and the transmission cover 5 are coupled, the male fitting surface 45 of the enlarged diameter portion 2sa of the pump shell 2s and the female fitting surface 47 of the peripheral wall portion 5a of the transmission cover 5 are fitted together. In addition, the front end surface of the peripheral wall portion 5a is brought into contact with the positioning step portion 46 of the enlarged diameter portion 2sa. Thereafter, a fillet weld 52 extending over the entire circumference is formed between the distal end surface of the peripheral wall portion 5a and the outer peripheral surface of the enlarged diameter portion 2sa. Thus, the pump shell 2s and the transmission cover 5 are coupled to each other.

また拡径部２ｓａには，凹部４８を内周側から覆って，その内部を異物溜まり５１とする円筒状の覆い壁５０が延設されており，上記異物溜まり５１は，覆い壁５０の先端側で伝動カバー５の内部と連通している。   The enlarged diameter portion 2sa is provided with a cylindrical covering wall 50 that covers the concave portion 48 from the inner peripheral side and has the inside as a foreign matter reservoir 51. The foreign matter reservoir 51 is formed at the tip of the covering wall 50. It communicates with the inside of the transmission cover 5 on the side.

再び図１において，伝動カバー５は，周壁部５ａの外端から半径方向内方に直角に屈曲した外周環状側壁部５ｂと，この外周環状側壁部５ｂの内周端から中心側に向かうに従いタービン羽根車３側に近接する円錐状側壁部５ｃと，この円錐状側壁部５ｃの内周端から半径方向内方に外周環状側壁部５ｂと平行に延びる内周環状側壁部５ｄと，この内周環状側壁部５ｄの内周端に溶接により連設されるキャップ状のカバーハブ５ｈとを備えており，円錐状側壁部５ｃは，中間部に環状段部を全く持たない。またカバーハブ５ｈは，閉じた先端部を外周環状側壁部５ｂの外側面より軸方向外方に突出するように配置される。   In FIG. 1 again, the transmission cover 5 includes an outer peripheral annular side wall portion 5b bent at a right angle inward in the radial direction from the outer end of the peripheral wall portion 5a, and a turbine as it goes from the inner peripheral end of the outer peripheral annular side wall portion 5b toward the center side. A conical side wall portion 5c adjacent to the impeller 3 side, an inner peripheral annular side wall portion 5d extending inward in the radial direction from the inner peripheral end of the conical side wall portion 5c in parallel with the outer peripheral annular side wall portion 5b; A cap-shaped cover hub 5h connected to the inner peripheral end of the annular side wall portion 5d by welding is provided, and the conical side wall portion 5c does not have an annular step portion at the middle. The cover hub 5h is arranged so that the closed tip end protrudes outward in the axial direction from the outer surface of the outer peripheral annular side wall 5b.

伝動カバー５の外周環状側壁部５ｂの内側面は，切削加工により環状の駆動摩擦面３５に形成される。また伝動カバー５の外側面には，前記円錐状側壁部５ｃにより，カバーハブ５ｈを囲繞する円錐状の凹部５ｆが画成される。   The inner side surface of the outer peripheral annular side wall portion 5b of the transmission cover 5 is formed on the annular drive friction surface 35 by cutting. A conical recess 5f surrounding the cover hub 5h is defined on the outer surface of the transmission cover 5 by the conical side wall 5c.

伝動カバー５の周壁部５ａ外周面には，前記環状薄肉部４９（図２参照）と外周環状側壁部５ｂとの間で始動用のリングギヤ７が嵌合して溶接され，このリングギヤ７に，エンジンのクランク軸１の端面にボルト９で結合した駆動板８がボルト９′で固着される。駆動板８は，概ね伝動カバー５の外側面に沿うように形成されており，クランク軸１の端部及びボルト９の頭部は，伝動カバー５外側面の前記凹部５ｆに受容される。特に，凹部５ｆの最深部にボルト９の頭部が配置される。またクランク軸１の端面には，袋状の位置決め孔１ａが設けられており，この位置決め孔１ａに前記カバーハブ５ｈが嵌合される。   A starting ring gear 7 is fitted and welded to the outer peripheral surface of the peripheral wall portion 5a of the transmission cover 5 between the annular thin wall portion 49 (see FIG. 2) and the outer peripheral annular side wall portion 5b. A drive plate 8 coupled with a bolt 9 is fixed to an end face of the crankshaft 1 of the engine with a bolt 9 '. The drive plate 8 is formed substantially along the outer surface of the transmission cover 5, and the end of the crankshaft 1 and the head of the bolt 9 are received in the recess 5 f on the outer surface of the transmission cover 5. In particular, the head of the bolt 9 is disposed at the deepest part of the recess 5f. A bag-like positioning hole 1a is provided on the end surface of the crankshaft 1, and the cover hub 5h is fitted into the positioning hole 1a.

タービン羽根車３のハブ，即ちタービンハブ３ｈと伝動カバー５との間にスラストニードルベアリング２６が介裝される。   A thrust needle bearing 26 is interposed between the hub of the turbine impeller 3, that is, the turbine hub 3 h and the transmission cover 5.

トルクコンバータＴの中心部にクランク軸１と同軸上に出力軸１０が配置される。この出力軸１０は，図示しない多段変速機の主軸となるもので，これにタービンハブ３ｈがスプライン嵌合される。また出力軸１０の端部は，軸受ブッシュ２３を介してカバーハブ５ｈに回転自在に支承される。   An output shaft 10 is disposed coaxially with the crankshaft 1 at the center of the torque converter T. The output shaft 10 is a main shaft of a multi-stage transmission (not shown), and a turbine hub 3h is spline-fitted thereto. The end of the output shaft 10 is rotatably supported by the cover hub 5h via the bearing bush 23.

出力軸１０の外周には，ステータ羽根車４のハブ４ｈ（以下，ステータハブ４ｈという。）をフリーホイール１１を介して支承する中空円筒状のステータ軸１２が配置され，これら出力軸１０及びステータ軸１２間には，それらの相対回転を許容する軸受ブッシュ１３が介裝される。ステータ軸１２の外端部はミッションケース１４に回転不能に支持される。   A hollow cylindrical stator shaft 12 for supporting a hub 4h of the stator impeller 4 (hereinafter referred to as a stator hub 4h) via a free wheel 11 is disposed on the outer periphery of the output shaft 10, and these output shaft 10 and stator shaft Between 12, a bearing bush 13 that allows relative rotation thereof is interposed. The outer end portion of the stator shaft 12 is supported by the transmission case 14 so as not to rotate.

フリーホイール１１は，ステータハブ４ｈの内周面に圧入により結合されるアウタレース１５と，ステータ軸１２の外周にスプライン結合されるインナレース１６と，これらレース１５，１６間に介裝される環状配列のスプラグ１７，１７…群とからなっている。ステータ羽根車４は，Ａｌ合金等の軽合金製であり，そのステータハブ４ｈの内周面に圧入されるアウタレース１５は鋼鉄製である。このアウタレース１５の一端面を支承すると共にスプラグ１７，１７…群の一端面に対向する端壁２７がステータハブ４ｈに一体に形成され，この端壁部２７とポンプ羽根車２のポンプハブ２ｈとの間にスラストニードルベアリング２９が介装される。   The free wheel 11 includes an outer race 15 coupled to the inner peripheral surface of the stator hub 4h by press-fitting, an inner race 16 splined to the outer periphery of the stator shaft 12, and an annular arrangement interposed between the races 15 and 16. It consists of sprags 17, 17. The stator impeller 4 is made of a light alloy such as an Al alloy, and the outer race 15 press-fitted into the inner peripheral surface of the stator hub 4h is made of steel. An end wall 27 that supports one end surface of the outer race 15 and faces one end surface of the sprags 17, 17... Is formed integrally with the stator hub 4 h, and is formed between the end wall portion 27 and the pump hub 2 h of the pump impeller 2. A thrust needle bearing 29 is interposed.

またステータハブ４ｈ内には，アウタレース１５の外端面に当接すると共にスプラグ１７，１７…群の他端面に対向する押さえ板２８が配置され，この押さえ板２８とタービンハブ３ｈとの間にスラストニードルベアリング２９′が介装される。   In the stator hub 4h, a pressing plate 28 that is in contact with the outer end surface of the outer race 15 and is opposed to the other end surface of the sprags 17, 17,... Is disposed, and a thrust needle bearing is provided between the pressing plate 28 and the turbine hub 3h. 29 'is interposed.

ステータ軸１２の外周には，ポンプ羽根車２に結合した補機駆動軸２０が相対回転可能に配置され，この補機駆動軸２０によって，トルクコンバータＴに作動オイルを供給するオイルポンプ２１が駆動されるようになっている。   An auxiliary machine drive shaft 20 coupled to the pump impeller 2 is disposed on the outer periphery of the stator shaft 12 so as to be relatively rotatable. An oil pump 21 that supplies hydraulic oil to the torque converter T is driven by the auxiliary machine drive shaft 20. It has come to be.

タービン羽根車３及び伝動カバー５には，前記循環回路６と外周部で連通するクラッチ油室２２画成され，このクラッチ油室２２には，タービン羽根車３及び伝動カバー５間を直結し得るロックアップクラッチＬが設けられる。即ち，ロックアップクラッチＬの主体をなすクラッチピストン２５が，クラッチ油室２２をタービン羽根車３側の内側室２２ａと伝動カバー５側の外側室２２ｂとに区画するようにクラッチ油室２２に配置される。   The turbine impeller 3 and the transmission cover 5 are defined by a clutch oil chamber 22 communicating with the circulation circuit 6 at the outer periphery, and the turbine impeller 3 and the transmission cover 5 can be directly connected to the clutch oil chamber 22. A lockup clutch L is provided. That is, the clutch piston 25 which forms the main body of the lockup clutch L is arranged in the clutch oil chamber 22 so as to partition the clutch oil chamber 22 into an inner chamber 22a on the turbine impeller 3 side and an outer chamber 22b on the transmission cover 5 side. Is done.

クラッチピストン２５は，伝動カバー５の周壁部５ａの内周面に近接する円筒状のリム部２５ａと，このリム部２５ａの外端から半径方向内方へ直角に屈曲した外周環状側壁部２５ｂと，この外周環状側壁部２５ｂの内周端から中心部に向かう従いタービン羽根車３に近接する円錐状側壁部２５ｃと，この円錐状側壁部２５ｃの内周端から半径方向内方に外周環状側壁部２５ｂと平行に延びる内周環状側壁部２５ｄと，この内周環状側壁部２５ｄの内周端に溶接されるピストンハブ２５ｈとから構成され，このクラッチピストン２５はタービン羽根車３の外側面に可及的に近接配置され，またこのクラッチピストン２５の外周環状側壁部２５ｂ，円錐状側壁部２５ｃ及び内周環状側壁部２５ｄに，前記伝動カバー５の外周環状側壁部５ｂ，円錐状側壁部５ｃ及び内周環状側壁部５ｄがそれぞれ近接して対向するように配置される。   The clutch piston 25 includes a cylindrical rim portion 25a that is close to the inner peripheral surface of the peripheral wall portion 5a of the transmission cover 5, an outer peripheral annular side wall portion 25b that is bent at a right angle radially inward from the outer end of the rim portion 25a, , A conical side wall portion 25c close to the turbine impeller 3 from the inner peripheral end of the outer peripheral annular side wall portion 25b toward the center, and an outer peripheral annular side wall radially inward from the inner peripheral end of the conical side wall portion 25c. The inner peripheral annular side wall portion 25d extending in parallel with the portion 25b and a piston hub 25h welded to the inner peripheral end of the inner peripheral annular side wall portion 25d are provided on the outer surface of the turbine impeller 3. The outer peripheral annular side wall portion 25b, the conical side wall portion 25c and the inner peripheral annular side wall portion 25d of the clutch piston 25 are arranged as close to each other as possible. Jo side wall 5c and the inner peripheral annular side wall portion 5d is disposed to face in close proximity, respectively.

クラッチピストン２５の外周環状側壁部２５ｂの外側面には，前記駆動摩擦面３５に対向する環状の摩擦ライニング３６が接着により形成されており，クラッチピストン２５は，その摩擦ライニング３６を駆動摩擦面３５に圧接させる接続位置と，その駆動摩擦面３５から離間する非接続位置との間を移動し得るように，ピストンハブ２５ｈをタービンハブ３ｈの外周面に摺動可能に支承されている。   An annular friction lining 36 facing the drive friction surface 35 is formed on the outer surface of the outer peripheral annular side wall 25b of the clutch piston 25 by adhesion. The clutch piston 25 attaches the friction lining 36 to the drive friction surface 35. The piston hub 25h is slidably supported on the outer peripheral surface of the turbine hub 3h so that the piston hub 25h can be moved between a connection position where the piston hub 25h is brought into pressure contact with and a non-connection position separated from the driving friction surface 35.

クラッチピストン２５のリム部２５ａ内には，クラッチピストン２５及びタービン羽根車３間を緩衝的に連結する公知のトルクダンパＤが配設される。   In the rim portion 25a of the clutch piston 25, a known torque damper D for bufferingly connecting the clutch piston 25 and the turbine impeller 3 is disposed.

出力軸１０の中心部には，横孔２４及びスラストニードルベアリング２６を介してクラッチ油室２２の外側室２２ｂに連通する第１油路４０が設けられる。また補機駆動軸２０とステータ軸１２との間には，前記スラストニードルベアリング２９を介して循環回路６の内周部に連通する第２油路４１が画成され，これら第１油路４０及び第２油路４１は，ロックアップ制御弁４２により，オイルポンプ２１の吐出側とオイル溜め４３とに交互に接続されるようになっている。   A first oil passage 40 that communicates with the outer chamber 22 b of the clutch oil chamber 22 through the lateral hole 24 and the thrust needle bearing 26 is provided at the center of the output shaft 10. Further, a second oil passage 41 communicating with the inner peripheral portion of the circulation circuit 6 via the thrust needle bearing 29 is defined between the auxiliary machine drive shaft 20 and the stator shaft 12. The second oil passage 41 is alternately connected to the discharge side of the oil pump 21 and the oil reservoir 43 by a lock-up control valve 42.

次に，この実施例の作用について説明する。   Next, the operation of this embodiment will be described.

エンジンのアイドリングないし極低速運転域では，ロックアップ制御弁４２は，図１に示すように，第１油路４０をオイルポンプ２１の吐出側に接続する一方，第２油路４１をオイル溜め４３に接続するように，図示しない電子制御ユニットにより制御される。したがって，エンジンのクランク軸１の出力トルクが駆動板８，伝動カバー５，ポンプ羽根車２へと伝達して，それを回転駆動し，更にオイルポンプ２１をも駆動すると，オイルポンプ２１の吐出作動オイルがロックアップ制御弁４２から第１油路４０，横孔２４及びスラストニードルベアリング２６，クラッチ油室２２の外側室２２ｂ，内側室２２ａを順次経て循環回路６に流入し，該回路６を満たした後，スラストニードルベアリング２９を経て第２油路４１に移り，ロックアップ制御弁４２からオイル溜め４３に還流する。   In the engine idling or extremely low speed operation region, the lockup control valve 42 connects the first oil passage 40 to the discharge side of the oil pump 21 and the second oil passage 41 as shown in FIG. It is controlled by an electronic control unit (not shown) so as to be connected to. Therefore, when the output torque of the crankshaft 1 of the engine is transmitted to the drive plate 8, the transmission cover 5, and the pump impeller 2 to rotate and drive the oil pump 21, the discharge operation of the oil pump 21 is performed. Oil flows from the lock-up control valve 42 to the circulation circuit 6 through the first oil passage 40, the lateral hole 24 and the thrust needle bearing 26, the outer chamber 22b of the clutch oil chamber 22, and the inner chamber 22a in this order. After that, it moves to the second oil passage 41 through the thrust needle bearing 29 and returns to the oil reservoir 43 from the lockup control valve 42.

而して，クラッチ油室２２では，上記のような作動オイルの流れにより外側室２２ｂの方が内側室２２ａよりも高圧となり，その圧力差によりクラッチピストン２５が伝動カバー５の駆動摩擦面３５から離れる方向へ押圧されるので，ロックアップクラッチＬは非接続状態となっており，ポンプ羽根車２及びタービン羽根車３の相対回転を許容している。したがって，クランク軸１からポンプ羽根車２が回転駆動されると，循環回路５を満たしている作動オイルが矢印のように循環回路５を循環することにより，ポンプ羽根車３の回転トルクをタービン羽根車４に伝達し，出力軸１０を駆動する。   Thus, in the clutch oil chamber 22, the outer chamber 22 b becomes higher in pressure than the inner chamber 22 a due to the flow of the working oil as described above, and the clutch piston 25 moves away from the drive friction surface 35 of the transmission cover 5 due to the pressure difference. Since it is pushed away, the lock-up clutch L is in a disconnected state and allows relative rotation of the pump impeller 2 and the turbine impeller 3. Therefore, when the pump impeller 2 is rotationally driven from the crankshaft 1, the working oil that fills the circulation circuit 5 circulates in the circulation circuit 5 as indicated by the arrows, thereby reducing the rotational torque of the pump impeller 3 to the turbine blade. This is transmitted to the car 4 to drive the output shaft 10.

このとき，ポンプ羽根車２及びタービン羽根車３間でトルクの増幅作用が生じていれば，それに伴う反力がステータ羽根車４に負担され，ステータ羽根車４は，フリーホイール１１のロック作用により，即ちスプラグ１７，１７…群がアウタレース１５及びインナレース１６の相対回転を阻止するように両レース１５，１６間にロックされることにより，ステータ軸１２に連結，固定される。   At this time, if a torque amplifying action is generated between the pump impeller 2 and the turbine impeller 3, the accompanying reaction force is borne by the stator impeller 4, and the stator impeller 4 is caused by the locking action of the freewheel 11. That is, the sprags 17, 17... Are connected and fixed to the stator shaft 12 by being locked between the races 15 and 16 so as to prevent relative rotation of the outer race 15 and the inner race 16.

トルク増幅作用を終えると，ステータ羽根車４は，これが受けるトルク方向の反転により，フリーホイール１１が空転すること，即ちスプラグ１７，１７…群が両レース１５，１６の相対回転を許容することでポンプ羽根車２及びタービン羽根車３と共に同一方向へ回転するようになる。   When the torque amplifying operation is finished, the stator impeller 4 is rotated by the reversal of the torque direction received by the stator impeller 4, that is, the sprags 17, 17... Allow the relative rotation of the races 15, 16. The pump impeller 2 and the turbine impeller 3 rotate in the same direction.

トルクコンバータＴがこのようなカップリング状態となったところで，電子制御ユニットによりロックアップ制御弁４２を切換える。その結果，オイルポンプ２１の吐出作動オイルは，先刻とは反対に，ロックアップ制御弁４２から第２油路４１を経て循環回路６に流入して，該回路６を満たした後，クラッチ油室２２の内側室２２ａに移って，該内側室２２ａをも満たす。一方，クラッチ油室２２の外側室２２ｂは，第１油路４０及びロックアップ制御弁４２を介してオイル溜め４３に開放されるので，クラッチ油室２２では，内側室２２ａの方が外側室２２ｂよりも高圧となり，クラッチピストン２５は，その圧力差により伝動カバー５側に押圧され，摩擦ライニング３６を伝動カバー５の駆動摩擦面３５に圧接させ，ロックアップクラッチＬは接続状態となる。すると，クランク軸１からポンプ羽根車２に伝達した回転トルクは，伝動カバー５からクラッチピストン２５，トルクダンパＤを介してタービン羽根車３に機械的に伝達することになるから，ポンプ羽根車２及びタービン羽根車４は直結の状態となり，クランク軸１の出力トルクを出力軸１０に効率良く伝達することができ，燃費の低減を図ることができる。   When the torque converter T enters such a coupling state, the lockup control valve 42 is switched by the electronic control unit. As a result, the oil discharged from the oil pump 21 flows from the lock-up control valve 42 to the circulation circuit 6 through the second oil passage 41 and fills the circuit 6, contrary to the previous operation. The inner chamber 22a is filled with the inner chamber 22a. On the other hand, the outer chamber 22b of the clutch oil chamber 22 is opened to the oil sump 43 via the first oil passage 40 and the lockup control valve 42. Therefore, in the clutch oil chamber 22, the inner chamber 22a is more in the outer chamber 22b. Due to the pressure difference, the clutch piston 25 is pressed toward the transmission cover 5 and the friction lining 36 is brought into pressure contact with the drive friction surface 35 of the transmission cover 5, and the lockup clutch L is connected. Then, the rotational torque transmitted from the crankshaft 1 to the pump impeller 2 is mechanically transmitted from the transmission cover 5 to the turbine impeller 3 via the clutch piston 25 and the torque damper D. The turbine impeller 4 is directly connected, and the output torque of the crankshaft 1 can be efficiently transmitted to the output shaft 10, thereby reducing fuel consumption.

トルクコンバータＴのこのような作動中，ポンプシェル２ｓ及び伝動カバー５の特に拡径部２ｓａ及び周壁部５ａには，遠心力及び内部圧力による半径方向の大なる荷重が加わり，ポンプシェル２ｓ及び伝動カバー５間の隅肉溶接部５２に応力が集中しようとするが，伝動カバー５の周壁部５ａには，その内周面の環状の凹部４８により，隅肉溶接部５２と反対側で雌嵌合面４７に隣接する環状薄肉部４９が設けられるので，この環状薄肉部４９が適度に撓むことにより，隅肉溶接部５２から環状薄肉部４９に応力が分散することになり，隅肉溶接部５２での過大応力の集中を効果的に緩和することができ，ポンプシェル２ｓ及び伝動カバー５の板厚を増すことなく，その耐久性の向上を図ることができる。   During such operation of the torque converter T, a large radial load due to centrifugal force and internal pressure is applied to the pump shell 2 s and the transmission cover 5, particularly the enlarged diameter portion 2 sa and the peripheral wall portion 5 a, and the pump shell 2 s and transmission Stress tends to concentrate on the fillet weld 52 between the covers 5, but the inner wall 5 a of the transmission cover 5 is fitted with a female fitting on the opposite side of the fillet weld 52 by an annular recess 48 on the inner peripheral surface. Since the annular thin portion 49 adjacent to the mating surface 47 is provided, when the annular thin portion 49 is appropriately bent, stress is distributed from the fillet welded portion 52 to the annular thin portion 49, and fillet welded. It is possible to effectively alleviate the concentration of excessive stress in the portion 52, and it is possible to improve the durability without increasing the plate thickness of the pump shell 2s and the transmission cover 5.

しかも環状薄肉部４９に隣接する雌嵌合面４７では周壁部５ａの肉厚の減少はないから，隅肉溶接部５２の溶接代を充分に確保し得て，隅肉溶接部５２の強度を高めることができる。   Moreover, since there is no reduction in the thickness of the peripheral wall portion 5a at the female fitting surface 47 adjacent to the annular thin portion 49, a sufficient welding allowance for the fillet welded portion 52 can be secured, and the strength of the fillet welded portion 52 can be increased. Can be increased.

また前記凹部４８の両内側面と底面とは，連続した曲面で構成されるので，前記環状薄肉部４９全体に応力を分散させて，該薄肉部４９の強度低下を防ぐことができる。   Further, since both the inner side surface and the bottom surface of the concave portion 48 are constituted by continuous curved surfaces, it is possible to disperse stress over the entire annular thin portion 49 and prevent the strength reduction of the thin portion 49.

またポンプシェル２ｓの拡径部２ｓａの端部には，前記凹部４８を内周側から覆って該凹部４８を袋状の異物溜まり５１にする環状の覆い壁５０が延設され，この覆い壁５０の先端側で前記異物溜まり５１がクラッチ油室２２に連通されるので，凹部４８を異物溜まり５１に利用して，トルクコンバータＴの作動中，作動オイルから遠心分離された異物を捕捉することができる。   Further, an annular covering wall 50 is provided at the end of the enlarged diameter portion 2sa of the pump shell 2s so as to cover the concave portion 48 from the inner peripheral side and make the concave portion 48 a bag-like foreign substance reservoir 51. Since the foreign substance reservoir 51 is communicated with the clutch oil chamber 22 at the tip end side of 50, the concave portion 48 is used for the foreign substance reservoir 51 to capture the foreign substance centrifugally separated from the working oil during operation of the torque converter T. Can do.

しかも前記覆い壁５０の外周面には，前記凹部４８に臨む環状の肉抜き部５０ａが形成されるので，前記異物溜まりの容積を増加させることができる。   In addition, since the annular thinned portion 50a facing the recess 48 is formed on the outer peripheral surface of the covering wall 50, the volume of the foreign substance reservoir can be increased.

さらに伝動カバー５の周壁部５ａの外周面の，前記環状薄肉部４９と伝動カバー５の外周環状側壁部５ｂとの間にはリングギア７が嵌合されて溶接されるので，周壁部５ａをリングギア７の取り付け部に利用し得ると共に，リングギア７の溶接による環状薄肉部４９の熱歪を防ぐことができる。   Further, since the ring gear 7 is fitted and welded between the annular thin wall portion 49 and the outer peripheral annular side wall portion 5b of the transmission cover 5 on the outer peripheral surface of the peripheral wall portion 5a of the transmission cover 5, the peripheral wall portion 5a is attached. It can be used for the attachment portion of the ring gear 7 and can prevent thermal distortion of the annular thin portion 49 due to welding of the ring gear 7.

また伝動カバー５には，駆動摩擦面３５を形成した外周環状側壁部５ｂとカバーハブ５ｈとの間を接続する，外周環状側壁部５ｂからカバーハブ５ｈに向うに従いタービン羽根車３に近接する円錐状側壁部５ｃが設けられ，その間には環状段部が存在しないから，大容量のロックアップクラッチＬ及びトルクダンパＤを収容すべく伝動カバー５を大径に形成する場合でも，その耐圧性が高く，内部の高油圧による伝動カバー５の軸方向の膨出変形を極力小さく抑えることができ，また応力集中を効果的に回避することができる。   Further, the transmission cover 5 is connected to the outer peripheral annular side wall portion 5b formed with the driving friction surface 35 and the cover hub 5h. The conical side wall is located closer to the turbine impeller 3 from the outer peripheral annular side wall portion 5b toward the cover hub 5h. Since the portion 5c is provided and there is no annular step portion therebetween, even when the transmission cover 5 is formed with a large diameter to accommodate the large-capacity lockup clutch L and the torque damper D, the pressure resistance is high, The bulge deformation in the axial direction of the transmission cover 5 due to the high hydraulic pressure can be suppressed as small as possible, and stress concentration can be effectively avoided.

しかも上記円錐状側壁部５ｃの外側面により画成される円錐状凹部５ｆには，クランク軸１の端部が受容されるのみならず，特に，該凹部５ｆの最深部には，クランク軸１の端面に駆動板８を結合するボルト９の頭部が収められるので，ボルト９の比較的背丈の高い頭部を採用して駆動板８のクランク軸１への大なる緊締力を確保しながら，トルクコンバータＴ及びエンジンの組立体の軸方向寸法の短縮化を図ることができ，その組立体のコンパクト化に寄与し得る。   Moreover, not only the end of the crankshaft 1 is received in the conical recess 5f defined by the outer surface of the conical side wall 5c, but in particular, the crankshaft 1 is located at the deepest portion of the recess 5f. Since the head of the bolt 9 that couples the drive plate 8 is housed on the end face of the bolt 9, a relatively high head of the bolt 9 is used to secure a large tightening force of the drive plate 8 to the crankshaft 1. The axial dimensions of the torque converter T and the engine assembly can be shortened, which can contribute to the compactness of the assembly.

またキャップ状のカバーハブ５ｈは，閉じた先端部を外周環状側壁部５ｂの外側面より軸方向外方に突出させていて，クランク軸１の端面中心部の袋状の位置決め孔１ａに嵌合されているから，クランク軸１端部の凹部５ｆへの突入と相俟ってカバーハブ５ｈと位置決め孔１ａとの嵌合深さを充分に確保することができる。   The cap-shaped cover hub 5h has a closed tip projecting axially outward from the outer surface of the outer peripheral side wall 5b and is fitted into a bag-like positioning hole 1a at the center of the end surface of the crankshaft 1. Therefore, the fitting depth between the cover hub 5h and the positioning hole 1a can be sufficiently secured in combination with the protrusion of the end of the crankshaft 1 into the recess 5f.

ロックアップクラッチＬのクラッチピストン２５には，環状の摩擦ライニング３６を形成した外周環状側壁部２５ｂとピストンハブ２５ｈとの間を接続する，円錐角度を前記伝動カバー５の円錐状側壁部５ｃと略同じくする円錐状側壁部２５ｃが設けられるので，伝動カバー５を，クラッチピストン２５と共に，タービン羽根車３に極力近接して配置することが可能となり，トルクコンバータＴのコンパクト化を図ることができる。   The clutch piston 25 of the lockup clutch L is connected to the outer peripheral annular side wall 25b formed with the annular friction lining 36 and the piston hub 25h. The cone angle is substantially the same as that of the conical side wall 5c of the transmission cover 5. Since the same conical side wall portion 25c is provided, the transmission cover 5 and the clutch piston 25 can be arranged as close as possible to the turbine impeller 3, and the torque converter T can be made compact.

また伝動カバー５に前記円錐状側壁部５ｃを設けたことで，伝動カバー５の外周部内側には，タービン羽根車３に干渉されない比較的大きな環状スペースをつくることができ，このスペースを利用して，比較的大容量のロックアップクラッチＬの摩擦係合部とトルクダンパＤを配設することができる。   Further, by providing the conical side wall 5c in the transmission cover 5, a relatively large annular space that is not interfered with the turbine impeller 3 can be formed inside the outer periphery of the transmission cover 5, and this space is utilized. Thus, the friction engagement portion of the lockup clutch L having a relatively large capacity and the torque damper D can be provided.

本発明は上記実施例に限定されるものではなく，その要旨を逸脱しない範囲で種々の設計変更が可能である。   The present invention is not limited to the above embodiment, and various design changes can be made without departing from the scope of the invention.

本発明の実施例に係る自動車用トルクコンバータの上半部縦断側面図。The upper half vertical side view of the torque converter for motor vehicles based on the Example of this invention. 図１の２部拡大図。FIG. 2 is an enlarged view of part 2 of FIG. 1.

符号の説明Explanation of symbols

Ｔ・・・・・・流体伝動装置（トルクコンバータ）
２・・・・・・ポンプ羽根車
２ｓ・・・・・ポンプシェル
２ｓａ・・・・拡径部
３・・・・・・タービン羽根車
５・・・・・・伝動カバー
５ａ・・・・・周壁部
５ｂ・・・・・側壁部（外周環状側壁部）
２２・・・・・油室（クラッチ油室）
４５・・・・・雄間面
４７・・・・・雌間面
４８・・・・・凹部
４９・・・・・環状薄肉部
５０・・・・・覆い壁
５１・・・・・異物溜まり
５２・・・・・隅肉溶接部
T ・ ・ ・ ・ ・ ・ Fluid transmission device (torque converter)
2 .... Pump impeller 2s ... Pump shell 2sa ... Diameter expansion part 3 .... Turbine impeller 5 ... Transmission cover 5a ...・ Surrounding wall part 5b ...... Side wall part (outer peripheral annular side wall part)
22 ... Oil chamber (clutch oil chamber)
45 ··· Male surface 47 ··· Female surface 48 ··· Concavity 49 ··· Thin annular portion 50 · · · Cover wall 51 · · · Foreign substance reservoir 52 ... Fillet welded part

Claims (5)

タービン羽根車（３）に対置されて，それとの間に作動オイルの循環回路（６）を画成するポンプ羽根車（２）のポンプシェル（２ｓ）の外周側端部に拡径部（２ｓａ）を延設し，この拡径部（２ｓａ）外周の雄嵌合面（４５）と，タービン羽根車（３）の背面との間に循環回路（６）に連通する油室（２２）を画成する円筒状の伝動カバー（５）の周壁部（５ａ）内周の雌嵌合面（４７）とを相互に嵌合し，前記周壁部（５ａ）の端面と前記拡径部（２ｓａ）の外周面との間に全周に亙る隅肉溶接部（５２）を形成することにより，ポンプシェル（２ｓ）及び伝動カバー（５）を相互に結合した流体伝動装置において， 前記周壁部（５ａ）の内周面に，前記隅肉溶接部（５２）と反対側で前記雌嵌合面（４７）と隣接する環状の凹部（４８）を形成して，この凹部（４８）に対応する伝動カバー（５）の部分を，その両側の部分より肉厚が薄い環状薄肉部（４９）となしたことを特徴とする流体伝動装置。   A diameter-enlarged portion (2sa) is disposed at the outer peripheral side end of the pump shell (2s) of the pump impeller (2) that is opposed to the turbine impeller (3) and defines a working oil circulation circuit (6) therebetween. ) And an oil chamber (22) communicating with the circulation circuit (6) is provided between the male fitting surface (45) on the outer periphery of the enlarged diameter portion (2sa) and the rear surface of the turbine impeller (3). The peripheral wall portion (5a) of the cylindrical transmission cover (5) defining the inner female fitting surface (47) is fitted to each other, and the end surface of the peripheral wall portion (5a) and the enlarged diameter portion (2sa) In the fluid transmission device in which the pump shell (2s) and the transmission cover (5) are connected to each other by forming a fillet weld (52) extending around the entire circumference between the outer peripheral surface of the An annular recess (4) adjacent to the female fitting surface (47) on the inner peripheral surface of 5a) on the side opposite to the fillet welded portion (52). ) To form, portions, fluid transmission device characterized by the thickness from both sides of the part is no thin thin annular portion (49) of the transmission cover corresponding to the recess (48) (5). 請求項１記載の流体伝動装置において，
前記拡径部（２ｓａ）の端部に，前記凹部（４８）を内周側から覆って該凹部（４８）を袋状の異物溜まり（５１）にする環状の覆い壁（５０）を延設し，この覆い壁（５０）の先端側で前記異物溜まり（５１）を前記油室（２２）に連通したことを特徴とする流体伝動装置。 The fluid transmission device according to claim 1,
An annular covering wall (50) is provided at the end of the enlarged diameter portion (2sa) so as to cover the concave portion (48) from the inner peripheral side and make the concave portion (48) a bag-like foreign substance reservoir (51). The fluid transmission device is characterized in that the foreign substance reservoir (51) communicates with the oil chamber (22) at the front end side of the covering wall (50). 請求項１又は２記載の流体伝動装置において，
前記凹部（４８）の両内側面と底面とを，連続した曲面で構成したことを特徴とする流体伝動装置。 The fluid transmission device according to claim 1 or 2,
A fluid transmission device characterized in that both the inner side surface and the bottom surface of the recess (48) are formed by continuous curved surfaces. 請求項１〜３の何れかに記載の流体伝動装置において，
前記覆い壁（５０）の外周面に，前記凹部（４８）に臨む環状の肉抜き部（５０ａ）を形成したことを特徴とする流体伝動装置。 In the fluid transmission device according to any one of claims 1 to 3,
The fluid transmission device according to claim 1, wherein an annular thinned portion (50a) facing the concave portion (48) is formed on the outer peripheral surface of the covering wall (50). 請求項１〜４記載の流体伝動装置において，
前記周壁部（５ａ）の外周面の，前記環状薄肉部（４９）と伝動カバー（５）の側壁部（５ｂ）との間にリングギヤ（７）を嵌合して溶接したことを特徴とする流体伝動装置。 In the fluid transmission device according to claims 1 to 4,
A ring gear (7) is fitted and welded between the annular thin part (49) and the side wall part (5b) of the transmission cover (5) on the outer peripheral surface of the peripheral wall part (5a). Fluid transmission device.
JP2005080200A 2004-06-22 2005-03-18 Fluid transmission device Expired - Fee Related JP4537871B2 (en)

Priority Applications (2)

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JP2005080200A JP4537871B2 (en) 2005-03-18 2005-03-18 Fluid transmission device
US11/157,158 US7284645B2 (en) 2004-06-22 2005-06-21 Fluid transmission device

Applications Claiming Priority (1)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014101965A (en) * 2012-11-21 2014-06-05 Aisin Kiko Co Ltd Drive plate and ring gear member of drive plate

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62106053U (en) * 1985-12-25 1987-07-07
JP2003343690A (en) * 2002-05-23 2003-12-03 Yutaka Giken Co Ltd Torque converter
JP2005009607A (en) * 2003-06-20 2005-01-13 Valeo Unisia Transmission Kk Torque converter

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62106053U (en) * 1985-12-25 1987-07-07
JP2003343690A (en) * 2002-05-23 2003-12-03 Yutaka Giken Co Ltd Torque converter
JP2005009607A (en) * 2003-06-20 2005-01-13 Valeo Unisia Transmission Kk Torque converter

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014101965A (en) * 2012-11-21 2014-06-05 Aisin Kiko Co Ltd Drive plate and ring gear member of drive plate

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