JP5330277B2 - Fluid transmission device with lock-up clutch - Google Patents

Fluid transmission device with lock-up clutch Download PDF

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Publication number
JP5330277B2
JP5330277B2 JP2010006744A JP2010006744A JP5330277B2 JP 5330277 B2 JP5330277 B2 JP 5330277B2 JP 2010006744 A JP2010006744 A JP 2010006744A JP 2010006744 A JP2010006744 A JP 2010006744A JP 5330277 B2 JP5330277 B2 JP 5330277B2
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clutch
end wall
transmission cover
annular
wall portion
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JP2011144882A (en
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喜久 杉村
宏 水野
悟 門谷
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Yutaka Giken Co Ltd
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Yutaka Giken Co Ltd
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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
    • F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
    • 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
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch

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Description

本発明は、入力軸に連結される伝動カバーと、この伝動カバーに結合されるポンプインペラと、このポンプインペラとの間に作動オイルの循環回路を画成するよう配置され、且つ伝動カバーに背面を覆われると共に出力軸に連結されるタービンランナと、前記伝動カバー及びタービンランナ間に配設されるロックアップクラッチとを備え、そのロックアップクラッチを、前記伝動カバーに固着されるクラッチアウタと、このクラッチアウタに囲繞されて前記タービンランナに連結されるクラッチインナと、前記クラッチアウタに軸方向往復動可能に嵌合されるクラッチピストンと、前記クラッチアウタ及びクラッチインナ間に設けられ、前記クラッチピストンの往動によりクラッチアウタ及びクラッチインナ間を摩擦連結し、その復動によりクラッチアウタ及びクラッチインナ間の摩擦連結を解除する摩擦連結手段とで構成し、前記クラッチアウタが、前記クラッチピストン及び摩擦連結手段の外周を覆う筒状部と、この筒状部の一端から半径方向内向きに延びて前記伝動カバーの端壁の内面に重ね合わされ、溶接される環状端壁部とよりなる、ロックアップクラッチ付き流体伝動装置の改良に関する。   The present invention has a transmission cover coupled to an input shaft, a pump impeller coupled to the transmission cover, and a hydraulic oil circulation circuit defined between the pump impeller and the rear surface of the transmission cover. And a lockup clutch disposed between the transmission cover and the turbine runner, the clutch outer being fixed to the transmission cover, A clutch inner surrounded by the clutch outer and connected to the turbine runner; a clutch piston fitted to the clutch outer so as to be capable of reciprocating in the axial direction; and the clutch piston provided between the clutch outer and the clutch inner. The clutch outer and clutch inner are frictionally connected by the forward movement of the A friction coupling means for releasing the frictional connection between the latch outer and the clutch inner, the clutch outer covering the outer periphery of the clutch piston and the friction coupling means, and a radially inner portion from one end of the cylindrical part. The present invention relates to an improvement in a fluid transmission device with a lock-up clutch that extends in a direction and is overlapped with an inner surface of an end wall of the transmission cover and welded to an annular end wall portion.

かゝるロックアップクラッチ付き流体伝動装置は、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。   Such a fluid transmission device with a lock-up clutch is already known as disclosed in, for example, Patent Document 1 below.

特開２００８−１７５３３８号公報JP 2008-175338 A

従来、かゝるロックアップクラッチ付き流体伝動装置では、クラッチアウタの環状端壁部と伝動カバーの端壁とは、溶接により同心配置の二条の環状溶け込み部を形成することにより強固に結合していた。   Conventionally, in such a fluid transmission device with a lock-up clutch, the annular end wall portion of the clutch outer and the end wall of the transmission cover are firmly joined by forming two concentric annular penetration portions by welding. It was.

ところで、ロックアップクラッチ付き流体伝動装置におけるクラッチアウタの筒状部には、クラッチピストンが摺動自在に嵌装されるシリンダが形成されているので、上記のように、クラッチアウタの環状端壁部と伝動カバーの端壁とを、同心状配置の二条の環状溶け込み部の形成により結合するものでは、外側の環状溶け込み部が上記シリンダに必然的に近づくことになり、その外側の環状溶け込み部の形成時、シリンダに熱歪みを生じさせる可能性があり、そのような歪みの発生は、クラッチピストンの摺動性を妨げる一因となる。また二条の溶け込み部の形成は、溶接工程を多くしたり、溶接装置を大型化することになり、コストの低減を困難にしていた。   Incidentally, since the cylinder portion of the clutch outer in the fluid transmission device with the lock-up clutch is formed with a cylinder in which the clutch piston is slidably fitted, as described above, the annular end wall portion of the clutch outer is formed. And the end wall of the transmission cover are formed by the formation of two concentric annular penetration portions, the outer annular penetration portion inevitably approaches the cylinder. When formed, there is a possibility of causing thermal distortion in the cylinder, and the occurrence of such distortion is one factor that hinders the slidability of the clutch piston. Further, the formation of the two melted portions increases the number of welding processes and increases the size of the welding apparatus, making it difficult to reduce costs.

本発明は、かゝる事情に鑑みてなされたもので、クラッチアウタのシリンダを有する筒状部から極力離れた箇所で、一条の環状溶け込み部の形成によりクラッチアウタを伝動カバーに強固に結合してシリンダに熱歪みを生じさせず、そしてコストダウンを可能にするロックアップクラッチ付き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 the clutch outer is firmly connected to the transmission cover by forming a single annular melted portion at a position as far as possible from the cylindrical portion having the clutch outer cylinder. An object of the present invention is to provide a fluid transmission device with a lock-up clutch that does not cause thermal distortion in the cylinder and can reduce costs.

上記目的を達成するために、本発明は、入力軸に連結される伝動カバーと、この伝動カバーに結合されるポンプインペラと、このポンプインペラとの間に作動オイルの循環回路を画成するよう配置され、且つ伝動カバーに背面を覆われると共に出力軸に連結されるタービンランナと、前記伝動カバー及びタービンランナ間に配設されるロックアップクラッチとを備え、そのロックアップクラッチを、前記伝動カバーに固着されるクラッチアウタと、このクラッチアウタに囲繞されて前記タービンランナに連結されるクラッチインナと、前記クラッチアウタに軸方向往復動可能に嵌合されるクラッチピストンと、前記クラッチアウタ及びクラッチインナ間に設けられ、前記クラッチピストンの往動によりクラッチアウタ及びクラッチインナ間を摩擦連結し、その復動によりクラッチアウタ及びクラッチインナ間の摩擦連結を解除する摩擦連結手段とで構成し、前記クラッチアウタが、前記クラッチピストン及び摩擦連結手段の外周を覆う筒状部と、この筒状部の一端から半径方向内向きに延びて前記伝動カバーの端壁の内面に重ね合わされる環状端壁部とよりなり、前記環状端壁部と伝動カバーとの合わせ部を、レーザ溶接により形成される一条の環状溶接ビードによって結合する、ロックアップクラッチ付き流体伝動装置であって、前記伝動カバーの端壁に、前記環状端壁部を重ね合わせる第１内面と、前記環状端壁部の内周端面の一部に嵌合して前記伝動カバー及びクラッチアウタを同心上に保持する環状の位置決め肩部と、この位置決め肩部の端縁から半径方向内方に延びる第２内面とを形成し、前記位置決め肩部から露出した前記環状端壁部の内周端面と前記第２内面とで囲まれる内隅部から該内隅部の略二等分線に沿いながら前記環状端壁部の内周端面と位置決め肩部との嵌合部、並びに前記環状端壁部と伝動カバーの端壁部との合わせ部を越えて前記伝動カバーの端壁の中間深さに達する、レーザ溶接による環状溶接ビードを形成したことを第１の特徴とする。 In order to achieve the above object, the present invention defines a hydraulic oil circulation circuit between a transmission cover coupled to an input shaft, a pump impeller coupled to the transmission cover, and the pump impeller. A turbine runner that is disposed on the rear surface of the transmission cover and connected to the output shaft; and a lockup clutch that is disposed between the transmission cover and the turbine runner, and the lockup clutch is connected to the transmission cover. A clutch outer fixed to the clutch outer, a clutch inner surrounded by the clutch outer and coupled to the turbine runner, a clutch piston fitted to the clutch outer so as to be capable of reciprocating in the axial direction, the clutch outer and the clutch inner Between the clutch outer and the clutch inner due to the forward movement of the clutch piston. And a frictional connection means for releasing the frictional connection between the clutch outer and the clutch inner by its backward movement, and the clutch outer includes a cylindrical portion covering the outer periphery of the clutch piston and the frictional connection means, An annular end wall portion extending radially inward from one end of the cylindrical portion and superimposed on the inner surface of the end wall of the transmission cover, and the mating portion of the annular end wall portion and the transmission cover is formed by laser welding. A fluid transmission device with a lock-up clutch that is coupled by a single annular weld bead formed, a first inner surface that overlaps the end wall of the transmission cover with the end wall of the transmission cover, An annular positioning shoulder that is fitted to a part of the inner peripheral end surface to hold the transmission cover and the clutch outer concentrically, and extends radially inward from an edge of the positioning shoulder. Forming an inner surface and extending from the inner corner portion surrounded by the inner peripheral end surface of the annular end wall portion exposed from the positioning shoulder portion and the second inner surface along a substantially bisector of the inner corner portion Reaching the intermediate depth of the end wall of the transmission cover over the fitting portion between the inner peripheral end surface of the end wall portion and the positioning shoulder, and the mating portion of the annular end wall portion and the end wall portion of the transmission cover; The first feature is that an annular weld bead is formed by laser welding.

また本発明は、入力軸に連結される伝動カバーと、この伝動カバーに結合されるポンプインペラと、このポンプインペラとの間に作動オイルの循環回路を画成するよう配置され、且つ伝動カバーに背面を覆われると共に出力軸に連結されるタービンランナと、前記伝動カバー及びタービンランナ間に配設されるロックアップクラッチとを備え、そのロックアップクラッチを、前記伝動カバーに固着されるクラッチアウタと、このクラッチアウタに囲繞されて前記タービンランナに連結されるクラッチインナと、前記クラッチアウタに軸方向往復動可能に嵌合されるクラッチピストンと、前記クラッチアウタ及びクラッチインナ間に設けられ、前記クラッチピストンの往動によりクラッチアウタ及びクラッチインナ間を摩擦連結し、その復動によりクラッチアウタ及びクラッチインナ間の摩擦連結を解除する摩擦連結手段とで構成し、前記クラッチアウタが、前記クラッチピストン及び摩擦連結手段の外周を覆う筒状部と、この筒状部の一端から半径方向内向きに延びて前記伝動カバーの端壁の内面に重ね合わされる環状端壁部とよりなり、前記環状端壁部と伝動カバーとの合わせ部を、レーザ溶接により形成される一条の環状溶接ビードによって結合する、ロックアップクラッチ付き流体伝動装置であって、前記伝動カバーの端壁に、前記環状端壁部を重ね合わせる第１内面と、前記環状端壁部の内周端面に嵌合して前記伝動カバー及びクラッチアウタを同心上に保持する環状の位置決め肩部と、この位置決め肩部の端縁から半径方向内方に延びる第２内面とを形成する一方、前記環状端壁部の内面に該環状端壁部の内周端寄りで半径方向内向きの円筒面を形成し、この円筒面と、この円筒面から半径方向内方に延びる前記環状端壁部の内面とで囲まれる内隅部から該内隅部の略二等分線に沿いながら前記環状端壁部と前記伝動カバーの端壁部との合わせ部を越えて前記伝動カバーの端壁の中間深さに達する、レーザ溶接による環状溶接ビードを形成したことを第２の特徴とする。 The present invention also includes a transmission cover coupled to the input shaft, a pump impeller coupled to the transmission cover, and a hydraulic oil circulation circuit defined between the pump impeller and the transmission cover. A turbine runner having a back surface and coupled to an output shaft; and a lockup clutch disposed between the transmission cover and the turbine runner, the clutch outer being fixed to the transmission cover; A clutch inner surrounded by the clutch outer and coupled to the turbine runner; a clutch piston fitted to the clutch outer so as to be capable of reciprocating in the axial direction; and the clutch outer and the clutch inner. The clutch outer and clutch inner are frictionally connected by the forward movement of the piston, And a friction coupling means for releasing the frictional connection between the clutch outer and the clutch inner. The clutch outer has a cylindrical portion that covers the outer periphery of the clutch piston and the friction coupling means, and a radius from one end of the cylindrical portion. A ring-shaped end weld that is formed by laser welding, and includes an annular end wall that extends inward in the direction and overlaps the inner surface of the end wall of the transmission cover. A fluid transmission device with a lock-up clutch that is coupled by a bead, wherein the fluid transmission device has a first inner surface that overlaps the end wall of the transmission cover and an inner peripheral end surface of the annular end wall. Forming an annular positioning shoulder for concentrically holding the transmission cover and the clutch outer, and a second inner surface extending radially inward from an edge of the positioning shoulder, A radially inward cylindrical surface is formed near the inner peripheral end of the annular end wall portion on the inner surface of the annular end wall portion, and the cylindrical surface and the annular end wall portion extending radially inward from the cylindrical surface An intermediate portion of the end wall of the transmission cover, passing along the substantially bisector of the inner corner from the inner corner surrounded by the inner surface, beyond the joint between the annular end wall and the end wall of the transmission cover The second feature is that an annular weld bead is formed by laser welding reaching the depth.

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、また前記入力軸はクランク軸１にそれぞれ対応する。   The fluid transmission device corresponds to a torque converter T in an embodiment of the present invention described later, and the input shaft corresponds to the crankshaft 1.

本発明の第１の特徴によれば、伝動カバーの端壁部に、クラッチアウタの環状端壁部の内周端面の一部に嵌合して伝動カバー及びクラッチアウタを同心上に保持する環状の位置決め肩部を形成したことで、伝動カバー及びクラッチアウタを相互に同心状態に保持することができる。しかも一条の環状溶接ビードが、位置決め肩部から露出した環状端壁部の内周端面と伝動カバー端壁部の第２内面とで囲まれる内隅部から該内隅部の略二等分線に沿いながら環状端壁部の内周端面及び位置決め肩部の嵌合部、並びに前記環状端壁部及び第１内面の合わせ部を越えて伝動カバーの端壁部の中間深さに達するように形成されるので、環状端壁部と伝動カバーの端壁部との間には、半径方向に比較的大きく広がる環状の溶接面と、軸方向に広がる環状の溶接面とを得ることができ、これらによりクラッチアウタ及び伝動カバー間を強固に結合することができて、大なるトルク伝達に耐えることができる。 According to the first aspect of the present invention, the end wall portion of the transmission cover is fitted to a part of the inner peripheral end surface of the annular end wall portion of the clutch outer to hold the transmission cover and the clutch outer concentrically. By forming the positioning shoulder, the transmission cover and the clutch outer can be held concentrically with each other. In addition, an annular weld bead is substantially bisected from the inner corner surrounded by the inner peripheral end surface of the annular end wall exposed from the positioning shoulder and the second inner surface of the transmission cover end wall. So as to reach the intermediate depth of the end wall portion of the transmission cover over the inner peripheral end surface of the annular end wall portion and the fitting portion of the positioning shoulder portion and the mating portion of the annular end wall portion and the first inner surface. Since it is formed, between the annular end wall portion and the end wall portion of the transmission cover, it is possible to obtain an annular welding surface that spreads relatively large in the radial direction and an annular welding surface that spreads in the axial direction, As a result, the clutch outer and the transmission cover can be firmly connected to each other and can withstand a large torque transmission.

しかも前記内隅部は、シリンダを有する筒状部より充分に離れているので、内隅部からの環状溶接ビードの形成時、シリンダに熱歪みを与えることを避けることができる。その際、環状溶接ビードの形成には、入熱が比較的少ないレーザ溶接が使用されることで、シリンダへの熱歪みの影響を一層少ないものとすることができる。   Moreover, since the inner corner is sufficiently separated from the cylindrical portion having the cylinder, it is possible to avoid applying thermal strain to the cylinder when forming the annular weld bead from the inner corner. In that case, the influence of the thermal distortion to a cylinder can be made still smaller by using laser welding with comparatively little heat input for formation of an annular weld bead.

また前記環状溶接ビードは、クラッチアウタ及び伝動カバー間に液密の結合部を形成して、油圧室からの油圧漏れを防ぎ、ロックアップクラッチの良好な接続状態を確保することができる。   Further, the annular weld bead can form a liquid-tight coupling portion between the clutch outer and the transmission cover to prevent hydraulic leakage from the hydraulic chamber and to ensure a good connection state of the lockup clutch.

さらに前記環状溶接ビードは、たった一条であるから、最少の溶接工程と、簡素な溶接装置をもってそれを可能にし、コストの低減をもたらすことができる。   Furthermore, since the annular weld bead is only a single line, it can be achieved with a minimum welding process and a simple welding apparatus, resulting in cost reduction.

また本発明の第２の特徴によれば、伝動カバーの端壁部に、クラッチアウタの環状端壁部を重ね合わせる第１内面と、環状端壁部の内周端面に嵌合して伝動カバー及びクラッチアウタを同心上に保持する環状の位置決め肩部を形成したことで、伝動カバー及びクラッチアウタを相互に同心状態に保持することができる。しかも前記第１の特徴と同様に、環状端壁部と伝動カバーの端壁部との間には、半径方向に比較的大きく広がる環状の溶接面と、軸方向に広がる環状の溶接面とを得ることができるから、クラッチアウタ及び伝動カバー間を強固に結合することができる。その他、前記第１の特徴による場合と同様に、クラッチアウタの筒状部での熱歪み防止及びコストの低減をもたらすことができる。 According to a second aspect of the present invention, the end wall of the transmission cover, and a first inner surface overlaying the annular end wall portion of the clutch outer, transmission cover is fitted to the inner peripheral end surface of the annular end wall portion Since the annular positioning shoulder for holding the clutch outer concentrically is formed, the transmission cover and the clutch outer can be held concentrically with each other. In addition, similarly to the first feature, an annular weld surface that spreads relatively large in the radial direction and an annular weld surface that spreads in the axial direction are provided between the annular end wall portion and the end wall portion of the transmission cover. Thus, the clutch outer and the transmission cover can be firmly coupled. In addition, as in the case of the first feature, it is possible to prevent thermal distortion at the cylindrical portion of the clutch outer and reduce costs.

本発明の参考例に係る流体伝動装置の上半部縦断側面図。The upper half longitudinal section side view of the fluid power transmission device concerning a reference example of the present invention. 図１中のクラッチアウタ及び伝動カバーのレーザ溶接部及びその溶接要領を示す拡大縦断面図。FIG. 2 is an enlarged longitudinal sectional view showing a laser welded portion of a clutch outer and a transmission cover in FIG. 1 and a welding procedure thereof. 本発明の第１実施例を示す、図２との対応図。FIG. 3 is a view corresponding to FIG. 2 showing the first embodiment of the present invention. 本発明の第２実施例を示す、図２との対応図。FIG. 3 is a view corresponding to FIG. 2 showing a second embodiment of the present invention.

本発明の実施の形態を、添付図面に示す参考例並びに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 reference examples shown in the accompanying drawings and preferred embodiments of the present invention.

先ず、図１及び図２に示す参考例の説明より始める。 First, the description starts with the description of the reference example shown in FIGS.

図１において、トルクコンバータＴは、ポンプインペラ２と、それと対置されるタービンランナ３と、それらの内周部間に配置されるステータ４とを備え、これら三者２，３，４間に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。   In FIG. 1, the torque converter T includes a pump impeller 2, a turbine runner 3 opposed to the pump impeller 2, and a stator 4 disposed between the inner peripheral portions of the pump impeller 2. A circulation circuit 6 for power transmission by oil is defined.

ポンプインペラ２の外周部には伝動カバー５が溶接により一体的に結合される。この伝動カバー５は、一端部をポンプインペラ２の外周部に溶接される円筒部５ａと、この円筒部５ａの他端部に一体に連設されてタービンランナ３の背面を覆う端壁部５ｂとで構成され、その円筒部５ａの他端部側の外周面に始動用のリングギヤ７が溶接され、このリングギヤ７に、クランク軸１にボルト９で結合される駆動板８がボルト９′で固着される。   A transmission cover 5 is integrally connected to the outer periphery of the pump impeller 2 by welding. The transmission cover 5 has a cylindrical portion 5 a whose one end is welded to the outer peripheral portion of the pump impeller 2, and an end wall portion 5 b which is integrally connected to the other end of the cylindrical portion 5 a and covers the back surface of the turbine runner 3. The starting ring gear 7 is welded to the outer peripheral surface on the other end side of the cylindrical portion 5a, and a drive plate 8 coupled to the crankshaft 1 by a bolt 9 is connected to the ring gear 7 by a bolt 9 '. It is fixed.

トルクコンバータＴの中心部にクランク軸１と同軸上に並ぶ出力軸１０が配置される。伝動カバー５の端壁部５ｂには、その外方及び内方に突出する一対の第１及び第２ハブ５ｈ，５ｈ′が形成されており、上記出力軸１０は、それら第１及び第２ハブ５ｈ，５ｈ′に軸受ブッシュ１８ａ，１８ｂを介して回転自在に支承される。またタービンランナ３のハブ３ｈの端面と、伝動カバー５の第２ハブ５ｈの端面との間にスラストニードルベアリング１５が介装される。出力軸１０は図示しない多段変速機の主軸となる。   An output shaft 10 arranged coaxially with the crankshaft 1 is disposed at the center of the torque converter T. A pair of first and second hubs 5h and 5h 'projecting outward and inward are formed on the end wall portion 5b of the transmission cover 5, and the output shaft 10 includes the first and second hubs. The hubs 5h and 5h ′ are rotatably supported via bearing bushes 18a and 18b. A thrust needle bearing 15 is interposed between the end surface of the hub 3 h of the turbine runner 3 and the end surface of the second hub 5 h of the transmission cover 5. The output shaft 10 is a main shaft of a multi-stage transmission (not shown).

出力軸１０の外周には、ステータ４のハブ４ｈをフリーホイール１１を介して支承する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。フリーホイール１１は、ステータ４のハブ４ｈの一側面に開口する有底円筒状の嵌合孔１６に圧入されるアウタレース１１ａと、ステータ軸１２の外周面にスプライン嵌合するインナレース１１ｂと、これらアウタ及びインナレース１１ａ，１１ｂ間に介装される多数のスプラグ１１ｃとからなる公知のものである。   A cylindrical stator shaft 12 for supporting the hub 4h of the stator 4 via a free wheel 11 is disposed on the outer periphery of the output shaft 10, and relative rotation between the output shaft 10 and the stator shaft 12 is allowed. The bearing bush 13 is interposed. The outer end portion of the stator shaft 12 is supported by the transmission case 14 so as not to rotate. The free wheel 11 includes an outer race 11a that is press-fitted into a bottomed cylindrical fitting hole 16 that opens on one side surface of the hub 4h of the stator 4, an inner race 11b that is spline-fitted to the outer peripheral surface of the stator shaft 12, and the like. It is a well-known thing consisting of many sprags 11c interposed between the outer and inner races 11a and 11b.

ステータ４のハブ４ｈと、これに対向するタービンランナ３及びポンプインペラ２の各ハブ３ｈ，２ｈとの間には、フリーホイール１１を挟むように配置される第１及び第２スラストニードルベアリング３７，３７′がそれぞれ介裝される。   Between the hub 4h of the stator 4 and the hubs 3h, 2h of the turbine runner 3 and the pump impeller 2 opposed to the hub 4h, first and second thrust needle bearings 37 disposed so as to sandwich the free wheel 11; 37 'is interposed.

ステータ軸１２の外周には、ポンプインペラ２のハブ２ｈに一体に連設したポンプ軸２０が相対回転可能に配置され、このポンプ軸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（図示せず）が駆動される。   A pump shaft 20 integrally connected to the hub 2h of the pump impeller 2 is disposed on the outer periphery of the stator shaft 12 so as to be relatively rotatable. An oil pump that supplies hydraulic oil to the torque converter T by the pump shaft 20 (see FIG. (Not shown) is driven.

タービンランナ３及び伝動カバー５間にクラッチ・ダンパ室２２が画成され、このクラッチ・ダンパ室２２には、伝動カバー５及びタービンランナ３間を直結し得るロックアップクラッチＬと、このロックアップクラッチＬのロックアップ時、伝動カバー５及びタービンランナ３間の伝達トルクを緩衝するトルクダンパＤとが収容される。   A clutch / damper chamber 22 is defined between the turbine runner 3 and the transmission cover 5. The clutch / damper chamber 22 includes a lockup clutch L that can directly connect the transmission cover 5 and the turbine runner 3, and the lockup clutch. When L is locked up, the transmission cover 5 and the torque damper D for buffering the transmission torque between the turbine runner 3 are accommodated.

ロックアップクラッチＬは、伝動カバー５の端壁部５ｂの内面に結合されるクラッチアウタ２５を備える。このクラッチアウタ２５は、前記伝動カバー５より肉厚が薄い鋼板製で、一端を開放した筒状部２５ａと、この筒状部２５ａの他端から半径方向内方に延びる環状端壁部２５ｂとよりなっており、その環状端壁部２５ｂは、伝動カバー５の端壁部５ｂの内面に重ね合わされ、そして環状端壁部２５ｂの内周端面２５ｂ１と伝動カバー５の端壁部５ｂの内面とで囲まれる内隅部５０Ａで実施される次のようなレーザ溶接により環状端壁部２５ｂ及び端壁部５ｂ間は結合される。   The lockup clutch L includes a clutch outer 25 that is coupled to the inner surface of the end wall portion 5 b of the transmission cover 5. The clutch outer 25 is made of a steel plate that is thinner than the transmission cover 5, and has a cylindrical portion 25a that is open at one end, and an annular end wall portion 25b that extends radially inward from the other end of the cylindrical portion 25a. The annular end wall portion 25b is superimposed on the inner surface of the end wall portion 5b of the transmission cover 5, and the inner peripheral end surface 25b1 of the annular end wall portion 25b and the inner surface of the end wall portion 5b of the transmission cover 5 The annular end wall portion 25b and the end wall portion 5b are joined together by the following laser welding performed at the inner corner portion 50A surrounded by.

即ち、図２に示すように、先ず、クラッチアウタ２５及び伝動カバー５は、図示しない位置決め治具により、相互に同心状態に保持する。そしてレーザ溶接トーチ５１を、それからのレーザビーム５２の入射方向が内隅部５０Ａの略二等分線Ａに一致するように設置し、レーザ溶接トーチ５１から内隅部５０Ａにレーザビーム５２を入射しつゝ、クラッチアウタ２５及び伝動カバー５を一体にそれらの中心軸線Ｘ（図１参照）周りに一回転させる。かくして、レーザ溶接による一条の環状溶接ビード５３が内隅部５０Ａから上記略二等分線Ａに沿いながら環状端壁部２５ｂと伝動カバー５の端壁部５ｂとの合わせ部を越えて伝動カバー５の端壁部５ｂの中間深さに達するまで形成される。この一条の環状溶接ビード５３により環状端壁部２５ｂ及び端壁部５ｂ間は結合される。   That is, as shown in FIG. 2, first, the clutch outer 25 and the transmission cover 5 are held concentrically with each other by a positioning jig (not shown). Then, the laser welding torch 51 is installed so that the incident direction of the laser beam 52 from the laser welding torch 51 coincides with the substantially bisector A of the inner corner portion 50A, and the laser beam 52 is incident on the inner corner portion 50A from the laser welding torch 51. As a result, the clutch outer 25 and the transmission cover 5 are integrally rotated around their central axis X (see FIG. 1). Thus, the single annular weld bead 53 formed by laser welding extends along the substantially bisector A from the inner corner portion 50A and beyond the joint portion between the annular end wall portion 25b and the end wall portion 5b of the transmission cover 5. 5 until the intermediate depth of the end wall portion 5b is reached. The annular end wall portion 25b and the end wall portion 5b are coupled to each other by the single annular weld bead 53.

クラッチアウタ２５の筒状部２５ａは、環状端壁部２５ｂに連なる小径部２５ａ１と、この小径部２５ａ１に環状段部を介して連なると共に開放端を有する大径部２５ａ２とで構成され、小径部２５ａ１の内周面にはシリンダ２７が、大径部２５ａ２の内周面には雌スプライン３８が形成される。そのシリンダ２７には、Ｏリング２８を介して軸方向往復動可能に嵌合されるクラッチピストン２９の外周部が摺動自在に嵌装され、その内周部は、伝動カバー５の前記第２ハブ５ｈの外周面にＯリング３２を介して摺動可能に支承される。   The cylindrical portion 25a of the clutch outer 25 is composed of a small diameter portion 25a1 connected to the annular end wall portion 25b, and a large diameter portion 25a2 connected to the small diameter portion 25a1 via an annular step portion and having an open end. A cylinder 27 is formed on the inner peripheral surface of 25a1, and a female spline 38 is formed on the inner peripheral surface of the large diameter portion 25a2. The cylinder 27 is slidably fitted with an outer peripheral portion of a clutch piston 29 fitted so as to be capable of reciprocating in the axial direction via an O-ring 28, and the inner peripheral portion thereof is the second portion of the transmission cover 5. It is slidably supported on the outer peripheral surface of the hub 5h via an O-ring 32.

クラッチアウタ２５の大径部２５ａ２内には、それと同心状にクラッチインナ２６が配置される。このクラッチインナ２６は、タービンランナ３の背面と、タービンランナ３にリベット３３により固着される支持板３４との間において、その支持板３４に形成される環状肩部３４ａの外周面に回転可能に支承される。このクラッチインナ２６はトルクダンパＤを介してタービンランナ３に連結される。このクラッチインナ２６の外周には雄スプライン３９が形成される。   A clutch inner 26 is disposed concentrically within the large diameter portion 25a2 of the clutch outer 25. The clutch inner 26 is rotatable between the rear surface of the turbine runner 3 and a support plate 34 fixed to the turbine runner 3 by a rivet 33 on the outer peripheral surface of an annular shoulder 34 a formed on the support plate 34. Supported. The clutch inner 26 is connected to the turbine runner 3 via a torque damper D. A male spline 39 is formed on the outer periphery of the clutch inner 26.

前記雌スプライン３８には複数枚の駆動摩擦板４０と、これらの外側に配置される１枚の受圧板４１とが摺動自在にスプライン嵌合され、その受圧板４１の外側方への移動を阻止する止環４２が雌スプライン３８の内周面に係止される。また雄スプライン３９には、上記駆動摩擦板４０及び受圧板４１と交互に重ねられる複数枚の従動摩擦板４３が摺動自在にスプライン嵌合される。上記駆動摩擦板４０、受圧板４１、止環４２及び従動摩擦板４３により前記摩擦連結手段３１が構成される。   A plurality of drive friction plates 40 and a single pressure receiving plate 41 arranged outside these are spline-fitted to the female spline 38 so as to be slidable, and the pressure receiving plate 41 moves outward. A stop ring 42 for blocking is locked to the inner peripheral surface of the female spline 38. Further, a plurality of driven friction plates 43 alternately stacked with the driving friction plates 40 and the pressure receiving plates 41 are slidably fitted to the male spline 39 in a slidable manner. The driving friction plate 40, the pressure receiving plate 41, the retaining ring 42, and the driven friction plate 43 constitute the friction coupling means 31.

伝動カバー５及びクラッチピストン２９間には油圧室４４が画成される。この油圧室４４において、クラッチピストン２９の軸方向往復動を許容しつゝクラッチアウタ２５及びクラッチピストン２９相互を回転方向に連結する回転連結手段３０が設けられる。   A hydraulic chamber 44 is defined between the transmission cover 5 and the clutch piston 29. The hydraulic chamber 44 is provided with a clutch outer 25 and a rotary coupling means 30 for coupling the clutch piston 29 in the rotational direction while allowing the clutch piston 29 to reciprocate in the axial direction.

この回転連結手段３０は、伝動カバー５及びクラッチピストン２９の対向面の一方に溶接される内歯ギヤ部材３５と、それら対向面の他方に溶接され内歯ギヤ部材３５に軸方向摺動自在に係合する外歯ギヤ部材３６とで構成される。   The rotation coupling means 30 is welded to one of the facing surfaces of the transmission cover 5 and the clutch piston 29, and is welded to the other of the facing surfaces and is slidable in the axial direction to the internal gear member 35. It is comprised with the external gear member 36 to engage.

クラッチピストン２９の前面には、それに隣接する駆動摩擦板４０に向かって開口する環状のばね収容溝４５が形成され、このばね収容溝４５に、クラッチピストン２９の前面より突出して駆動摩擦板４０に接する、皿ばねよりなるクッションばね４６が収容される。   An annular spring housing groove 45 that opens toward the adjacent drive friction plate 40 is formed on the front surface of the clutch piston 29, and projects from the front surface of the clutch piston 29 to the drive friction plate 40. A cushion spring 46 made of a disc spring is in contact therewith.

而して、油圧室４４に油圧を供給すれば、クラッチピストン２９は、受圧板４１に向かって軸方向に往動し、受圧板４１と協働して駆動摩擦板４０及び従動摩擦板４３を相互に圧接させるので、これら駆動摩擦板４０及び従動摩擦板４３を介してクラッチアウタ２５及びクラッチインナ２６間を摩擦連結することができる。即ち、ロックアップクラッチＬの接続状態を得ることができる。また油圧室４４から油圧を解放すれば、クラッチピストン２９は、クラッチ・ダンパ室２２の油圧により上記と反対に軸方向に復動するので、駆動摩擦板４０及び従動摩擦板４３から圧接力が解放され、クラッチアウタ２５及びクラッチインナ２６間の摩擦連結を解除することができる。即ち、ロックアップクラッチＬの遮断状態を得ることができる。   Thus, when hydraulic pressure is supplied to the hydraulic chamber 44, the clutch piston 29 moves forward in the axial direction toward the pressure receiving plate 41, and cooperates with the pressure receiving plate 41 to drive the drive friction plate 40 and the driven friction plate 43. Since they are pressed against each other, the clutch outer 25 and the clutch inner 26 can be frictionally connected via the drive friction plate 40 and the driven friction plate 43. That is, the connected state of the lockup clutch L can be obtained. If the hydraulic pressure is released from the hydraulic chamber 44, the clutch piston 29 is moved back in the axial direction opposite to the above by the hydraulic pressure of the clutch / damper chamber 22, so that the pressure contact force is released from the drive friction plate 40 and the driven friction plate 43. Thus, the frictional connection between the clutch outer 25 and the clutch inner 26 can be released. In other words, the disengaged state of the lockup clutch L can be obtained.

前記トルクダンパＤは、前記クラッチインナ２６にリベット６４により固着されて前記クラッチアウタ２５より半径方向外方に延びるばね保持板６６を備える。このばね保持板６６は、クラッチアウタ２５の外周面を囲繞する断面コ字状で環状のばね収容部６７を一体に有しており、このばね収容部６７内に、コイルばねよりなる複数のダンパばね６８が環状に配置され、各隣接するダンパばね６８間には、ばね収容部６７にリベット６５により固着される断面コ字状の駆動爪７０と、タービンランナ３の背面に溶接される従動爪７１とが配置される。これら駆動爪７０及び従動爪７１は、タービンランナ３の回転方向に沿って相対回転が可能であり、それらの相対回転によりダンパばね６８が圧縮され、駆動爪７０及び従動爪７１間の伝達トルクを緩衝するようになっている。駆動爪７０及び従動爪７１の相対回転時、ばね保持板６６に連結したクラッチインナ２６は、タービンランナ３に固着された前記支持板３４の環状肩部３４ａ周りに回転することになる。ばね保持板６６には、従動爪７１と干渉しない位置でダンパばね６８の外側面を押えて、それのばね収容部６７からの離脱を防ぐ押え板７２が固着される。   The torque damper D includes a spring holding plate 66 that is fixed to the clutch inner 26 with a rivet 64 and extends radially outward from the clutch outer 25. The spring holding plate 66 integrally has an annular spring accommodating portion 67 having a U-shaped cross section surrounding the outer peripheral surface of the clutch outer 25, and a plurality of dampers made of coil springs are provided in the spring accommodating portion 67. A spring 68 is arranged in an annular shape, and between each adjacent damper spring 68, a driving claw 70 having a U-shaped cross section fixed to the spring accommodating portion 67 by a rivet 65 and a driven claw welded to the back surface of the turbine runner 3. 71 are arranged. The driving claw 70 and the driven claw 71 can be rotated relative to each other along the rotational direction of the turbine runner 3, and the damper spring 68 is compressed by the relative rotation of the driving claw 70 and the driven claw 71. It is designed to buffer. When the driving claw 70 and the driven claw 71 are rotated relative to each other, the clutch inner 26 connected to the spring holding plate 66 rotates around the annular shoulder 34 a of the support plate 34 fixed to the turbine runner 3. The spring holding plate 66 is fixed with a presser plate 72 that presses the outer surface of the damper spring 68 at a position where it does not interfere with the driven claw 71 and prevents its release from the spring accommodating portion 67.

次に、この参考例の作用について説明する。 Next, the operation of this reference example will be described.

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、ポンプインペラ２へと伝達して、それを回転駆動し、更に図示しないオイルポンプをも駆動する。そのオイルポンプから吐出された作動オイルは循環回路６に供給される。   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 it, and also drive an oil pump (not shown). The working oil discharged from the oil pump is supplied to the circulation circuit 6.

エンジンのアイドリングないし極低速運転域では、ロックアップクラッチＬの油圧室４４は、図示しないロックアップ制御弁によりがオイル溜め（図示せず。）に解放される。したがって前述のように、ロックアップクラッチＬは遮断状態に置かれるので、循環回路６に供給された作動オイルは、ポンプインペラ２の回転に伴ない循環回路６を循環しながら、ポンプインペラ２の動力をタービンランナ３へと伝達する。   In an idling or extremely low speed operation region of the engine, the hydraulic chamber 44 of the lockup clutch L is released to an oil sump (not shown) by a lockup control valve (not shown). Therefore, as described above, the lock-up clutch L is placed in the disconnected state, so that the hydraulic oil supplied to the circulation circuit 6 circulates in the circulation circuit 6 as the pump impeller 2 rotates, Is transmitted to the turbine runner 3.

この間、ポンプインペラ２及びタービンランナ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４に負担され、ステータ４は、フリーホイール１１のロック作用により固定される。   During this time, if a torque amplifying action is generated between the pump impeller 2 and the turbine runner 3, the accompanying reaction force is borne by the stator 4, and the stator 4 is fixed by the locking action of the freewheel 11.

トルク増幅作用を終えると、ステータ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を空転させながらポンプインペラ２及びタービンランナ３と共に同一方向へ回転するようになる。   When the torque amplification operation is finished, the stator 4 rotates in the same direction together with the pump impeller 2 and the turbine runner 3 while the free wheel 11 is idling due to the reversal of the torque direction received by the stator 4.

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、図示しないロックアップ制御弁により、オイルポンプの吐出作動オイルがロックアップクラッチＬの油圧室４４にも供給され、その油圧によりクラッチピストン２９が往動し、クッションばね４６を介して駆動及び従動摩擦板４０，４３を受圧板４１に対して押圧することで、前述のようにロックアップクラッチＬは接続状態となり、ポンプインペラ２の回転トルクは、伝動カバー５から一条の環状溶接ビード５３を介してクラッチアウタ２５へ、さらに駆動及び従動摩擦板４０，４３及びトルクダンパＤを介してタービンランナ３へと機械的に伝達し、その伝動効率の向上を図ることができる。   When the torque converter T is in such a coupling state, the discharge operation oil of the oil pump is also supplied to the hydraulic chamber 44 of the lockup clutch L by a lockup control valve (not shown), and the hydraulic pressure causes the clutch piston 29 to move. By moving forward and pressing the driving and driven friction plates 40 and 43 against the pressure receiving plate 41 via the cushion spring 46, the lock-up clutch L is connected as described above, and the rotational torque of the pump impeller 2 is Then, the transmission is mechanically transmitted from the transmission cover 5 to the clutch outer 25 via the single annular weld bead 53, and further to the turbine runner 3 via the drive and driven friction plates 40 and 43 and the torque damper D, thereby improving the transmission efficiency. Can be achieved.

ところで、クラッチアウタ２５の環状端壁部２５ｂと伝動カバー５の端壁部５ｂとの間を結合する上記一条の環状溶接ビード５３は、環状端壁部２５ｂの内周端面２５ｂ１と伝動カバー５の端壁部５ｂの内面とで囲まれる内隅部５０Ａから該内隅部５０Ａの略二等分線Ａに沿いながら環状端壁部２５ｂと伝動カバー５の端壁部５ｂとの合わせ部を越えて前記伝動カバー５の端壁部５ｂの中間深さに達するよう、レーザ溶接により形成されるので、その環状溶接ビード５３は、一条であるにも拘らず、環状端壁部２５ｂと伝動カバー５の端壁部５ｂとの合わせ部には、環状端壁部２５ｂの内面に対する垂線に沿って溶け込み部を形成する場合に比して、大きく半径方向に広がる環状の溶接面Ｓを得ることができ、これによりクラッチアウタ２５及び伝動カバー５間を強固に結合することができ、大なるトルク伝達に耐えることができる。   By the way, the single annular weld bead 53 connecting the annular end wall portion 25b of the clutch outer 25 and the end wall portion 5b of the transmission cover 5 is formed between the inner peripheral end surface 25b1 of the annular end wall portion 25b and the transmission cover 5. The inner corner portion 50A surrounded by the inner surface of the end wall portion 5b extends from the inner corner portion 50A along the substantially bisector A of the inner corner portion 50A beyond the joining portion of the annular end wall portion 25b and the end wall portion 5b of the transmission cover 5. Since it is formed by laser welding so as to reach the intermediate depth of the end wall portion 5b of the transmission cover 5, the annular weld bead 53 has only one line, but the annular end wall portion 25b and the transmission cover 5 are formed. Compared with the case where the melted portion is formed along the perpendicular to the inner surface of the annular end wall portion 25b, an annular welding surface S that greatly expands in the radial direction can be obtained at the mating portion with the end wall portion 5b. Thus, the clutch outer 25 Between fine transmission cover 5 can be firmly attached, it can withstand large becomes torque transmission.

しかも前記内隅部５０Ａは、シリンダ２７を有する筒状部２５ａより充分に離れているので、内隅部５０Ａからの環状溶接ビード５３の形成時、シリンダ２７に熱歪みを与えることを避けることができる。その際、環状溶接ビード５３の形成には、入熱エネルギが比較的少ないレーザ溶接が使用されることで、シリンダ２７への熱歪みの影響を一層少ないものとすることができる。   Moreover, since the inner corner portion 50A is sufficiently separated from the cylindrical portion 25a having the cylinder 27, it is possible to avoid applying thermal distortion to the cylinder 27 when the annular weld bead 53 is formed from the inner corner portion 50A. it can. At that time, the formation of the annular weld bead 53 uses laser welding with relatively small heat input energy, so that the influence of thermal strain on the cylinder 27 can be further reduced.

また前記環状溶接ビード５３は、クラッチアウタ２５及び伝動カバー５間に液密の結合部を形成して、油圧室４４からの油圧漏れを防ぎ、ロックアップクラッチＬの良好な接続状態を確保することができる。   Further, the annular weld bead 53 forms a liquid-tight joint between the clutch outer 25 and the transmission cover 5 to prevent hydraulic leakage from the hydraulic chamber 44 and to ensure a good connection state of the lockup clutch L. Can do.

さらに前記環状溶接ビード５３は、たった一条であるから、最少の溶接工程と、簡素な溶接装置をもってそれを可能にし、コストの低減をもたらすことができる。   Furthermore, since the annular weld bead 53 is only a single line, it can be achieved with a minimum welding process and a simple welding apparatus, and the cost can be reduced.

次に、図３に示す本発明の第１実施例について説明する。 Next, a first embodiment of the present invention shown in FIG. 3 will be described.

この第１実施例では、伝動カバー５の端壁部５ｂに、クラッチアウタ２５の環状端壁部２５ｂを重ね合わせる第１内面５ｂ１と、上記環状端壁部２５ｂの内周端面２５ｂ１の一部に嵌合して伝動カバー５及びクラッチアウタ２５を同心上に保持する環状の位置決め肩部５ｂ２と、この位置決め肩部５ｂ２の端縁から半径方向内方に延びる第２内面５ｂ３とが形成される。而して、位置決め肩部５ｂ２から露出した環状端壁部２５ｂの内周端面２５ｂ１と第２内面５ｂ３とで囲まれる内隅部５０Ｂから内隅部５０Ｂの略二等分線Ａに沿いながら環状端壁部２５ｂの内周端面２５ｂ１及び位置決め肩部５ｂ２の嵌合部、並びに前記環状端壁部２５ｂ及び第１内面５ｂ１の合わせ部を越えて伝動カバー５の端壁部５ｂの中間深さに達する環状溶接ビード５３がレーザ溶接により形成される。 In the first embodiment, a first inner surface 5b1 that overlaps the end wall portion 5b of the transmission cover 5 with the annular end wall portion 25b of the clutch outer 25, and a part of the inner peripheral end surface 25b1 of the annular end wall portion 25b. An annular positioning shoulder 5b2 that fits to hold the transmission cover 5 and the clutch outer 25 concentrically and a second inner surface 5b3 that extends radially inward from the edge of the positioning shoulder 5b2 are formed. Thus, the annular end wall 25b exposed from the positioning shoulder 5b2 is annularly formed along the substantially bisector A between the inner corner 50B and the inner corner 50B surrounded by the inner peripheral end surface 25b1 and the second inner surface 5b3. To the intermediate depth of the end wall portion 5b of the transmission cover 5 beyond the fitting portion of the inner peripheral end surface 25b1 and the positioning shoulder portion 5b2 of the end wall portion 25b and the mating portion of the annular end wall portion 25b and the first inner surface 5b1. The reaching annular weld bead 53 is formed by laser welding.

その他の構成は、前記参考例と同様であるので、図３中、その参考例と対応する部分には同一の参照符号を付して、重複する説明を省略する。 The other configuration is the same as the previous SL reference example, in FIG. 3, the portions corresponding to that in Reference Example are denoted by the same reference numerals, and overlapping description is omitted.

この第１実施例によれば、伝動カバー５の端壁部５ｂに、クラッチアウタ２５の環状端壁部２５ｂの内周端面２５ｂ１の一部に嵌合して伝動カバー５及びクラッチアウタ２５を同心上に保持する環状の位置決め肩部５ｂ２を形成したことで、伝動カバー５及びクラッチアウタ２５を相互に同心状態に保持することができる。しかも一条の環状溶接ビード５３を、これが内隅部５０Ｂから内隅部５０Ｂの略二等分線Ａに沿いながら環状端壁部２５ｂの内周端面２５ｂ１と位置決め肩部５ｂ２との嵌合部、並びに前記環状端壁部２５ｂと伝動カバー５の端壁部５ｂとの合わせ部を越えて伝動カバー５の端壁部５ｂの中間深さに達するように形成することで、環状端壁部２５ｂと伝動カバー５の端壁部５ｂとの間には、半径方向に比較的大きく広がる環状の溶接面Ｓと、軸方向に広がる環状の溶接面Ｓ′とを得ることができ、これらによりクラッチアウタ２５及び伝動カバー５間を一層強固に結合することができ、大なるトルク伝達に耐えることができる。その他、前記参考例と同様に、クラッチアウタ２５の筒状部２５ａでの熱歪み防止及びコストの低減をもたらすことができる。 According to the first embodiment, the transmission cover 5 and the clutch outer 25 are concentrically fitted to the end wall portion 5b of the transmission cover 5 with a part of the inner peripheral end surface 25b1 of the annular end wall portion 25b of the clutch outer 25. By forming the annular positioning shoulder 5b2 to be held on, the transmission cover 5 and the clutch outer 25 can be held concentrically with each other. In addition, the annular weld bead 53 is connected to the inner peripheral end face 25b1 of the annular end wall 25b and the positioning shoulder 5b2 while being along the substantially bisector A from the inner corner 50B to the inner corner 50B. In addition, the annular end wall portion 25b and the end wall portion 5b of the transmission cover 5 are formed so as to reach the intermediate depth of the end wall portion 5b of the transmission cover 5 so as to reach the intermediate end wall portion 25b. Between the end wall portion 5b of the transmission cover 5, it is possible to obtain an annular welding surface S that expands relatively in the radial direction and an annular welding surface S ′ that extends in the axial direction. In addition, the transmission covers 5 can be more firmly connected to each other and can withstand a large torque transmission. In addition, similarly to the reference example, it is possible to prevent thermal distortion and reduce costs in the cylindrical portion 25a of the clutch outer 25.

最後に、図４に示す本発明の第２実施例について説明する。 Finally, a second embodiment of the present invention shown in FIG. 4 will be described.

この第２実施例では、伝動カバー５の端壁部５ｂに、クラッチアウタ２５の環状端壁部２５ｂを重ね合わせる第１内面５ｂ１と、環状端壁部２５ｂの内周端面２５ｂ１に嵌合して伝動カバー５及びクラッチアウタ２５を同心上に保持する環状の位置決め肩部５ｂ２と、この位置決め肩部５ｂ２の端縁から半径方向内方に延びる第２内面５ｂ３とが形成される。一方、環状端壁部２５ｂの内面には、環状端壁部２５ｂの内周端寄りで半径方向内向きの円筒面２５ｂ２が形成され、この円筒面２５ｂ２と、この円筒面２５ｂ２から半径方向内方に延びる環状端壁部２５ｂの内面とで囲まれる内隅部５０Ｃから内隅部５０Ｃの略二等分線Ａに沿いながら環状端壁部２５ｂと伝動カバー５の第１内面５ｂ１との合わせ部を越えて伝動カバー５の端壁部５ｂの中間深さに達する環状溶接ビード５３がレーザ溶接により形成される。その他の構成は、前記参考例と同様であるので、図４中、その参考例と対応する部分には同一の参照符号を付して、重複する説明を省略する。 In the second embodiment, the end wall portion 5b of the transmission cover 5 is fitted to the first inner surface 5b1 that overlaps the annular end wall portion 25b of the clutch outer 25 and the inner peripheral end surface 25b1 of the annular end wall portion 25b. An annular positioning shoulder 5b2 that concentrically holds the transmission cover 5 and the clutch outer 25 and a second inner surface 5b3 that extends radially inward from the edge of the positioning shoulder 5b2 are formed. On the other hand, on the inner surface of the annular end wall portion 25b, a radially inward cylindrical surface 25b2 is formed near the inner peripheral end of the annular end wall portion 25b. The cylindrical surface 25b2 and a radially inward direction from the cylindrical surface 25b2 The inner end portion 50C surrounded by the inner surface of the annular end wall portion 25b extends from the inner corner portion 50C along the substantially bisector A of the inner corner portion 50C, and the mating portion of the annular end wall portion 25b and the first inner surface 5b1 of the transmission cover 5 An annular weld bead 53 that reaches the intermediate depth of the end wall portion 5b of the transmission cover 5 is formed by laser welding. Other configurations, since the the same as the reference example, in FIG. 4, parts corresponding to the reference example are denoted by the same reference numerals, and overlapping description is omitted.

この第２実施例によれば、伝動カバー５の端壁部５ｂに、クラッチアウタ２５の環状端壁部２５ｂを重ね合わせる第１内面５ｂ１と、環状端壁部２５ｂの内周端面２５ｂ１に嵌合して伝動カバー５及びクラッチアウタ２５を同心上に保持する環状の位置決め肩部５ｂ２を形成したことで、伝動カバー５及びクラッチアウタ２５を相互に同心状態に保持することができる。その他、前記参考例と同様に、クラッチアウタ２５の筒状部２５ａでの熱歪み防止及びコストの低減をもたらすことができる。 According to this second embodiment, the end wall 5b of the transmission cover 5 is fitted to the first inner surface 5b1 that overlaps the annular end wall 25b of the clutch outer 25 and the inner peripheral end surface 25b1 of the annular end wall 25b. By forming the annular positioning shoulder 5b2 that concentrically holds the transmission cover 5 and the clutch outer 25, the transmission cover 5 and the clutch outer 25 can be held concentrically with each other. In addition, similarly to the reference example, it is possible to prevent thermal distortion and reduce costs in the cylindrical portion 25a of the clutch outer 25.

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 embodiments, and various design changes can be made without departing from the scope of the invention.

Ｌ・・・・・・ロックアップクラッチ
Ｔ・・・・・・流体伝動装置（トルクコンバータ）
１・・・・・・入力軸（クランク軸）
２・・・・・・ポンプインペラ
３・・・・・・タービンランナ
５・・・・・・伝動カバー
５ａ・・・・・円筒部
５ｂ・・・・・端壁部
５ｂ１・・・・第１内面
５ｂ２・・・・位置決め肩部
５ｂ３・・・・第２内面
６・・・・・・循環回路
２５・・・・・クラッチアウタ
２５ａ・・・・筒状部
２５ｂ・・・・環状端壁部
２５ｂ１・・・内周端面
２５ｂ２・・・円筒面
２６・・・・・クラッチインナ
２９・・・・・クラッチピストン
３１・・・・・摩擦連結手段
５０Ｂ，５０Ｃ・・・・内隅部
５３・・・・・環状溶接ビード L ... Lock-up clutch T ... Fluid transmission device (torque converter)
1. Input shaft (crankshaft)
2 .... Pump impeller 3 ... Turbine runner 5 ... Transmission cover 5a ... Cylindrical part 5b ... End wall part 5b1 ... 1 inner surface 5b2 ... positioning shoulder 5b3 ... second inner surface 6 ... circulation circuit 25 ... clutch outer 25a ... cylindrical portion 25b ... annular end Wall part 25b1 ... inner peripheral end face 25b2 ... cylindrical surface 26 ... clutch inner 29 ... clutch piston 31 ... friction coupling means 50B , 50C ... ... inner corner Part 53 ... Annular weld bead

Claims (2)

入力軸（１）に連結される伝動カバー（５）と、この伝動カバー（５）に結合されるポンプインペラ（２）と、このポンプインペラ（２）との間に作動オイルの循環回路（６）を画成するよう配置され、且つ伝動カバー（５）に背面を覆われると共に出力軸（１０）に連結されるタービンランナ（３）と、前記伝動カバー（５）及びタービンランナ（３）間に配設されるロックアップクラッチ（Ｌ）とを備え、そのロックアップクラッチ（Ｌ）を、前記伝動カバー（５）に固着されるクラッチアウタ（２５）と、このクラッチアウタ（２５）に囲繞されて前記タービンランナ（３）に連結されるクラッチインナ（２６）と、前記クラッチアウタ（２５）に軸方向往復動可能に嵌合されるクラッチピストン（２９）と、前記クラッチアウタ（２５）及びクラッチインナ（２６）間に設けられ、前記クラッチピストン（２９）の往動によりクラッチアウタ（２５）及びクラッチインナ（２６）間を摩擦連結し、その復動によりクラッチアウタ（２５）及びクラッチインナ（２６）間の摩擦連結を解除する摩擦連結手段（３１）とで構成し、前記クラッチアウタ（２５）が、前記クラッチピストン（２９）及び摩擦連結手段（３１）の外周を覆う筒状部（２５ａ）と、この筒状部（２５ａ）の一端から半径方向内向きに延びて前記伝動カバー（５）の端壁部（５ｂ）の内面に重ね合わされる環状端壁部（２５ｂ）とよりなり、前記環状端壁部（２５ｂ）と伝動カバー（５）との合わせ部を、レーザ溶接により形成される一条の環状溶接ビード（５３）によって結合する、ロックアップクラッチ付き流体伝動装置であって、
前記伝動カバー（５）の端壁部（５ｂ）に、前記環状端壁部（２５ｂ）を重ね合わせる第１内面（５ｂ１）と、前記環状端壁部（２５ｂ）の内周端面（２５ｂ１）の一部に嵌合して前記伝動カバー（５）及びクラッチアウタ（２５）を同心上に保持する環状の位置決め肩部（５ｂ２）と、この位置決め肩部（５ｂ２）の端縁から半径方向内方に延びる第２内面（５ｂ３）とを形成し、前記位置決め肩部（５ｂ２）から露出した前記環状端壁部（２５ｂ）の内周端面（２５ｂ１）と前記第２内面（５ｂ３）とで囲まれる内隅部（５０Ｂ）から該内隅部（５０Ｂ）の略二等分線（Ａ）に沿いながら前記環状端壁部（２５ｂ）の内周端面（２５ｂ１）と位置決め肩部（５ｂ２）との嵌合部、並びに前記環状端壁部（２５ｂ）と伝動カバー（５）の端壁部（５ｂ）との合わせ部を越えて前記伝動カバー（５）の端壁部（５ｂ）の中間深さに達する、レーザ溶接による環状溶接ビード（５３）を形成したことを特徴とする、ロックアップクラッチ付き流体伝動装置。 A hydraulic oil circuit (6) is connected between the transmission cover (5) connected to the input shaft (1), the pump impeller (2) coupled to the transmission cover (5), and the pump impeller (2). Between the transmission cover (5) and the turbine runner (3), the rear surface of the transmission cover (5) being covered and the output shaft (10) being connected. A lockup clutch (L) disposed on the transmission cover (5), and the lockup clutch (L) is surrounded by the clutch outer (25) fixed to the transmission cover (5) and the clutch outer (25). A clutch inner (26) coupled to the turbine runner (3), a clutch piston (29) fitted to the clutch outer (25) so as to be capable of reciprocating in the axial direction, and the clutch outer (2 ) And the clutch inner (26), and the clutch outer (25) and the clutch inner (26) are frictionally connected by the forward movement of the clutch piston (29), and the clutch outer (25) and the clutch And a frictional coupling means (31) for releasing the frictional coupling between the inner (26), and the clutch outer (25) covers the outer periphery of the clutch piston (29) and the frictional coupling means (31). (25a) and an annular end wall portion (25b) that extends radially inward from one end of the cylindrical portion (25a) and is superimposed on the inner surface of the end wall portion (5b) of the transmission cover (5). becomes, the annular end wall portion and a mating portion of the transmission cover (5) (25b), joined by Ichijo annular weld bead formed by laser welding (53), the lock-up class A Chi hydraulic power transmission with,
A first inner surface (5b1) for overlapping the annular end wall portion (25b) on the end wall portion (5b) of the transmission cover (5), and an inner peripheral end surface (25b1) of the annular end wall portion (25b). An annular positioning shoulder (5b2) that fits in part and holds the transmission cover (5) and the clutch outer (25) concentrically, and radially inward from the edge of the positioning shoulder (5b2) A second inner surface (5b3) extending from the inner peripheral end surface (25b1) of the annular end wall portion (25b) exposed from the positioning shoulder (5b2) and the second inner surface (5b3). The inner peripheral end surface (25b1) of the annular end wall portion (25b) and the positioning shoulder portion (5b2) along the substantially bisector (A) of the inner corner portion (50B) from the inner corner portion (50B). fitting portion, and an end of the annular end wall portion (25b) and the transmission cover (5) A lock formed by forming an annular weld bead (53) by laser welding that reaches the intermediate depth of the end wall (5b) of the transmission cover (5) beyond the joint with the portion (5b) Fluid transmission device with up clutch. 入力軸（１）に連結される伝動カバー（５）と、この伝動カバー（５）に結合されるポンプインペラ（２）と、このポンプインペラ（２）との間に作動オイルの循環回路（６）を画成するよう配置され、且つ伝動カバー（５）に背面を覆われると共に出力軸（１０）に連結されるタービンランナ（３）と、前記伝動カバー（５）及びタービンランナ（３）間に配設されるロックアップクラッチ（Ｌ）とを備え、そのロックアップクラッチ（Ｌ）を、前記伝動カバー（５）に固着されるクラッチアウタ（２５）と、このクラッチアウタ（２５）に囲繞されて前記タービンランナ（３）に連結されるクラッチインナ（２６）と、前記クラッチアウタ（２５）に軸方向往復動可能に嵌合されるクラッチピストン（２９）と、前記クラッチアウタ（２５）及びクラッチインナ（２６）間に設けられ、前記クラッチピストン（２９）の往動によりクラッチアウタ（２５）及びクラッチインナ（２６）間を摩擦連結し、その復動によりクラッチアウタ（２５）及びクラッチインナ（２６）間の摩擦連結を解除する摩擦連結手段（３１）とで構成し、前記クラッチアウタ（２５）が、前記クラッチピストン（２９）及び摩擦連結手段（３１）の外周を覆う筒状部（２５ａ）と、この筒状部（２５ａ）の一端から半径方向内向きに延びて前記伝動カバー（５）の端壁部（５ｂ）の内面に重ね合わされる環状端壁部（２５ｂ）とよりなり、前記環状端壁部（２５ｂ）と伝動カバー（５）との合わせ部を、レーザ溶接により形成される一条の環状溶接ビード（５３）によって結合する、ロックアップクラッチ付き流体伝動装置であって、
前記伝動カバー（５）の端壁部（５ｂ）に、前記環状端壁部（２５ｂ）を重ね合わせる第１内面（５ｂ１）と、前記環状端壁部（２５ｂ）の内周端面（２５ｂ１）に嵌合して前記伝動カバー（５）及びクラッチアウタ（２５）を同心上に保持する環状の位置決め肩部（５ｂ２）と、この位置決め肩部（５ｂ２）の端縁から半径方向内方に延びる第２内面（５ｂ３）とを形成する一方、前記環状端壁部（２５ｂ）の内面に該環状端壁部（２５ｂ）の内周端寄りで半径方向内向きの円筒面（２５ｂ２）を形成し、この円筒面（２５ｂ２）と、この円筒面（２５ｂ２）から半径方向内方に延びる前記環状端壁部（２５ｂ）の内面とで囲まれる内隅部（５０Ｃ）から該内隅部（５０Ｃ）の略二等分線（Ａ）に沿いながら前記環状端壁部（２５ｂ）と前記伝動カバー（５）の端壁部（５ｂ）との合わせ部を越えて前記伝動カバー（５）の端壁部（５ｂ）の中間深さに達する、レーザ溶接による環状溶接ビード（５３）を形成したことを特徴とする、ロックアップクラッチ付き流体伝動装置。 A hydraulic oil circuit (6) is connected between the transmission cover (5) connected to the input shaft (1), the pump impeller (2) coupled to the transmission cover (5), and the pump impeller (2). Between the transmission cover (5) and the turbine runner (3), the rear surface of the transmission cover (5) being covered and the output shaft (10) being connected. A lockup clutch (L) disposed on the transmission cover (5), and the lockup clutch (L) is surrounded by the clutch outer (25) fixed to the transmission cover (5) and the clutch outer (25). A clutch inner (26) coupled to the turbine runner (3), a clutch piston (29) fitted to the clutch outer (25) so as to be capable of reciprocating in the axial direction, and the clutch outer (2 ) And the clutch inner (26), and the clutch outer (25) and the clutch inner (26) are frictionally connected by the forward movement of the clutch piston (29), and the clutch outer (25) and the clutch And a frictional coupling means (31) for releasing the frictional coupling between the inner (26), and the clutch outer (25) covers the outer periphery of the clutch piston (29) and the frictional coupling means (31). (25a) and an annular end wall portion (25b) that extends radially inward from one end of the cylindrical portion (25a) and is superimposed on the inner surface of the end wall portion (5b) of the transmission cover (5). A lock-up club, in which the mating portion of the annular end wall (25b) and the transmission cover (5) is joined by a single annular weld bead (53) formed by laser welding. A Chi hydraulic power transmission with,
A first inner surface (5b1) for overlapping the annular end wall portion (25b) on the end wall portion (5b) of the transmission cover (5), and an inner peripheral end surface (25b1) of the annular end wall portion (25b). An annular positioning shoulder (5b2) that fits to hold the transmission cover (5) and the clutch outer (25) concentrically, and extends radially inward from an edge of the positioning shoulder (5b2). 2 forming an inner surface (5b3), on the inner surface of the annular end wall (25b) is formed a radially inward cylindrical surface (25b2) near the inner peripheral end of the annular end wall (25b), From the inner corner (50C) surrounded by the cylindrical surface (25b2) and the inner surface of the annular end wall (25b) extending radially inward from the cylindrical surface (25b2), the inner corner (50C) said annular end wall portion while along substantially a bisector (a) (25b) and before An annular weld bead (53) is formed by laser welding that reaches the intermediate depth of the end wall (5b) of the transmission cover (5) beyond the joint with the end wall (5b) of the transmission cover (5). A fluid transmission device with a lock-up clutch, characterized in that
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