JP2508957Y2 - Driving force transmission device - Google Patents
Driving force transmission deviceInfo
- Publication number
- JP2508957Y2 JP2508957Y2 JP1989092819U JP9281989U JP2508957Y2 JP 2508957 Y2 JP2508957 Y2 JP 2508957Y2 JP 1989092819 U JP1989092819 U JP 1989092819U JP 9281989 U JP9281989 U JP 9281989U JP 2508957 Y2 JP2508957 Y2 JP 2508957Y2
- Authority
- JP
- Japan
- Prior art keywords
- retainer
- rotating member
- pressing force
- friction clutch
- transmission device
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
Description
【考案の詳細な説明】 （産業上の利用分野） 本考案は、同軸的かつ相対回転可能に位置する内外両
回転部材間に配設されて、これら両部材間のトルク伝達
を行う駆動力伝達装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention is a drive force transmission device that is disposed between inner and outer rotary members that are coaxially and relatively rotatable and that transmits torque between these members. Regarding the device.
（従来技術） かかる駆動力伝達装置は、駆動側回転部材と従動側回
転部材間に配設されてこれら両部材の相対回転時これら
両部材を互にトルク伝達可能に連結して、従動側回転部
材を駆動させる連結機構として使用されるものと、駆動
側および従動側回転部材間、両駆動側回転部材間または
両従動側回転部材間に配設されてこれら両部材の相対回
転時これら両部材を互にトルク伝達可能に連結して、こ
れら両部材間の回転差を制限させる差動制限機構として
使用されるもの等に大別される。前者の連結機構は主と
してリヤルタイム式の四輪駆動車における一方の動力伝
達系路に配設され、また後者の差動制限機構は主として
車両における各ディファレンシャルに配設される。(Prior Art) Such a driving force transmission device is disposed between a driving-side rotating member and a driven-side rotating member, and when both these members rotate relative to each other, the two members are coupled to each other so that torque can be transmitted to the driven-side rotating member. A member used as a connecting mechanism for driving members, a driving-side driven member, a driven-side rotating member, both driving-side rotating members, or both driven-side rotating members. Are connected to each other so that torque can be transmitted, and are used as a differential limiting mechanism for limiting the rotational difference between these two members. The former coupling mechanism is mainly disposed on one power transmission line in a real-time four-wheel drive vehicle, and the latter differential limiting mechanism is mainly disposed on each differential of the vehicle.
しかして、従来の駆動力伝達装置としては特開昭63-2
40429号公報に示されているように、同軸的かつ相対回
転可能に位置する内外両回転部材間に配設され、これら
両回転部材の相対回転により作動して利用回転部材をト
ルク伝達可能に連結する摩擦係合力を発生させるととも
に付与される軸方向の押圧力に応じて前記摩擦係合力を
増減させる摩擦クラッチ、および両回転部材の相対回転
に応じた軸方向の押圧力を発生させて前記摩擦クラッチ
に付与する押圧力発生手段を備え、同押圧力発生手段
を、前記両回転部材間に液密的に軸方向へ摺動可能かつ
外側回転部材に一体回転可能に組付けられて一側を前記
摩擦クラッチに当接する作動ピストンと、前記外側回転
部材の開口端部に一体回転可能に設けられて前記作動ピ
ストンの他側との間に軸方向に所定間隔を有して粘性流
体が封入される流体室を形成するリテーナと、半径方向
へ延びる１または複数のベーン部を備え前記流体室にて
前記内側回転部材に一体的に組付けられたロータとによ
り構成してなる駆動力伝達装置がある。Thus, as a conventional driving force transmission device, Japanese Patent Laid-Open No. 63-2
As disclosed in Japanese Patent No. 40429, it is arranged between both inner and outer rotary members that are coaxially and relatively rotatably positioned, and is operated by relative rotation of these both rotary members to connect the use rotary member so that torque can be transmitted. Friction friction force that increases or decreases the frictional engagement force according to the axial pressing force that is applied, and an axial pressing force that corresponds to the relative rotation of both rotating members to generate the frictional force. A pressing force generating means to be applied to the clutch is provided, and the pressing force generating means is liquid-tightly slidable in the axial direction between the rotating members and is integrally rotatably mounted on the outer rotating member so that one side can be rotated. A viscous fluid is sealed between the working piston that comes into contact with the friction clutch and the other end of the working piston that is integrally rotatably provided at the opening end of the outer rotating member and has a predetermined axial distance. Fluid chamber A retainer to form, there are one or more of at includes a vane portion the fluid chamber formed by constituted by a rotor assembled integrally to the inner rotary member driving force transmitting device extending radially.
この種形式の駆動力伝達装置においては、両回転部材
間に相対回転が生じると外側回転部材に一体回転可能に
組付けた作動ピストンおよびリテーナと、内側回転部材
に一体的に組付けたロータとの間に相対回転が生じ、流
体室の前記ロータのベーン部にて封入室内の粘性流体が
強制的に流動させられ、封入室内では流動抵抗等に起因
して圧力が発生する。すなわち、押圧力発生手段に差動
回転数に応じた圧力が発生する。この圧力は作動ピスト
ンを軸方向に押圧して摩擦クラッチを押圧させ、同クラ
ッチに両回転部材をトルク伝達可能に連結する摩擦係合
力を発生させる。かかる摩擦係合力は差動回転数に比例
し、両回転部材間では差動回転数に比例したトルクが一
方から他方へ伝達される。従って、当該駆動力伝達装置
は四輪駆動車の一方の動力伝達系路における駆動側回転
部材と従動側回転部材との連結機構として機能するとと
もに、駆動側および従動側回転部材間、両駆動側回転部
材間または両従動側回転部材間の差動制限機構としても
機能する。In this type of driving force transmission device, an actuating piston and a retainer that are integrally rotatable with an outer rotating member when a relative rotation occurs between both rotating members, and a rotor that is integrally assembled with an inner rotating member. Relative rotation occurs during this period, the viscous fluid in the sealed chamber is forced to flow in the vane portion of the rotor of the fluid chamber, and pressure is generated in the sealed chamber due to flow resistance and the like. That is, a pressure corresponding to the differential rotation speed is generated in the pressing force generating means. This pressure pushes the actuating piston in the axial direction to push the friction clutch, and the friction engagement force that connects both rotating members to the clutch so that torque can be transmitted is generated in the clutch. The frictional engagement force is proportional to the differential rotation speed, and torque proportional to the differential rotation speed is transmitted from one rotating member to the other rotating member. Therefore, the driving force transmission device functions as a connecting mechanism between the driving side rotation member and the driven side rotation member in one power transmission system path of the four-wheel drive vehicle, and also between the driving side and the driven side rotation member and both driving sides. It also functions as a differential limiting mechanism between rotating members or between both driven rotating members.
（考案が解決しようとする課題） ところで、上記した形式の駆動力伝達装置においては
作動ピストン、ロータおよびリテーナの３者によってロ
ータの両側に形成される微小間隙が押圧力の発生に大き
く影響するため、これらの微小間隙を精度よく設定する
ことが必要である。また、摩擦クラッチにおいても同ク
ラッチを構成する各クラッチプレートと各クラッチディ
スク間の微小間隙は摩擦係合力の発生に大きく影響する
ため、これらの微小間隙も精度よく設定することが必要
である。しかして、当該形式の駆動力伝達装置において
は、特に、摩擦クラッチの各クラッチプレートと各クラ
ッチディスクとの間の微小間隙を精度よく調整して、摩
擦クラッチのプレロードを精度よく設定すべき要請があ
る。従って、本考案の目的は当該形式の駆動力伝達装置
において、かかる要請に対処することにある。(Problems to be solved by the invention) By the way, in the driving force transmission device of the above-mentioned type, the minute gaps formed on both sides of the rotor by the working piston, the rotor and the retainer greatly affect the generation of the pressing force. It is necessary to accurately set these minute gaps. Further, also in the friction clutch, the minute gaps between the clutch plates and the clutch disks constituting the same clutch have a great influence on the generation of the frictional engagement force, and therefore it is necessary to set these minute gaps accurately. Therefore, in the driving force transmission device of this type, in particular, there is a demand that the minute gap between each clutch plate and each clutch disc of the friction clutch be accurately adjusted to accurately set the preload of the friction clutch. is there. Therefore, it is an object of the present invention to address such a need in a drive force transmission device of that type.
（課題を解決するための手段） 本考案は上記した形式の駆動力伝達装置において、前
記作動ピストンの他側に環状凹所を形成し、かつ前記外
側回転部材の開口端部の内周にネジ部を設けるとともに
前記リテーナの外端部の外周に前記ネジ部に進退可能に
螺着されるネジ部を設け、前記リテーナを前記外側回転
部材に螺着して前記作動ピストンの環状外緑面に当接さ
せて、同作動ピストンの他側にて前記環状凹所と前記リ
テーナ間に前記流体室を形成するとともに前記作動ピス
トンを介して前記摩擦クラッチのプレロードを調整し、
その後前記外側回転部材と前記リテーナをスポット溶接
にて互いに結合したことを特徴とするものである。(Means for Solving the Problems) The present invention provides a driving force transmission device of the type described above, wherein an annular recess is formed on the other side of the working piston, and a screw is formed on the inner periphery of the opening end of the outer rotating member. A threaded portion that is screwed to the threaded portion so as to be capable of advancing and retracting on the outer periphery of the outer end portion of the retainer, and the retainer is screwed to the outer rotating member to form an annular outer green surface of the working piston. Abutting to form the fluid chamber between the annular recess and the retainer on the other side of the working piston, and adjust the preload of the friction clutch via the working piston;
After that, the outer rotating member and the retainer are connected to each other by spot welding.
（考案の作用・効果） 本考案に係る駆動力伝達装置においては、外側回転部
材の開口端部にリテーナを螺着して作動ピストンの環状
外緑面に当接させて、作動ピストンの環状凹所とリテー
ナ間に流体室を形成するとともに作動ピストンを介して
摩擦クラッチのプレロードを調整しているので、リテー
ナからロータを介することなく直接作動ピストンに押圧
力が伝達され、押圧力発生手段における圧力特性に影響
を及ぼすことなく、摩擦クラッチのプレロードを精度よ
く調整することができる。(Operation and Effect of the Invention) In the driving force transmission device according to the present invention, the retainer is screwed to the opening end of the outer rotating member and brought into contact with the annular outer green surface of the operating piston to form the annular recess of the operating piston. Since the fluid chamber is formed between the place and the retainer and the preload of the friction clutch is adjusted via the working piston, the pressing force is directly transmitted from the retainer to the working piston without passing through the rotor, and the pressure in the pressing force generating means is increased. The preload of the friction clutch can be adjusted accurately without affecting the characteristics.
また、リテーナを螺着して摩擦クラッチのプレロード
を調整した後には、リテーナと外側回転部材とをスポッ
ト溶接にて互いに結合しているため、摩擦クラッチのプ
レロードの調整後にはリテーナが緩んでプレロードに変
動が生じることは全くない。Also, after adjusting the preload of the friction clutch by screwing the retainer, the retainer and the outer rotating member are connected to each other by spot welding, so the retainer loosens and becomes preloaded after adjusting the preload of the friction clutch. There is no fluctuation.
（実施例） 以下本考案の実施例を図面に基づいて説明するに、第
１図には本考案にかかる駆動力伝達装置の一実施例が示
されている。当該駆動力伝達装置10は第３図に示すよう
に、リヤルタイム式の四輪駆動車の後輪側動力伝達系路
に配設される。(Embodiment) An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows an embodiment of a driving force transmission device according to the present invention. As shown in FIG. 3, the driving force transmission device 10 is arranged in a rear wheel side power transmission system path of a real-time type four-wheel drive vehicle.
当該車両は前輪側が常時駆動するとともに後輪側が必
要時駆動するもので、エンジン21の一側に組付けたトラ
ンスアクスル22はトランスミッションおよびトランスフ
ァを備え、エンジン21からの駆動力をアクスルシャフト
23に出力して前輪24を駆動させるとともに、第１プロペ
ラシャフト25に出力する。第１プロペラシャフト25は駆
動力伝達装置10を介して第２プロペラシャフト26に連結
していて、これら両シャフト25、26がトルク伝達可能な
場合駆動力がリヤディファレンシャル27を介してアクス
ルシャフト28に出力され、後輪29が駆動する。In the vehicle, the front wheel side is always driven and the rear wheel side is driven when necessary.The transaxle 22 mounted on one side of the engine 21 is equipped with a transmission and a transfer, and the driving force from the engine 21 is transmitted to the axle shaft.
23 to drive the front wheels 24 and output to the first propeller shaft 25. The first propeller shaft 25 is connected to the second propeller shaft 26 via the driving force transmission device 10. When both the shafts 25, 26 can transmit torque, the driving force is transmitted to the axle shaft 28 via the rear differential 27. It is output and the rear wheels 29 are driven.
しかして、駆動力伝達装置10はアウタケース11および
インナシャフト12からなる環状の作動室内に押圧力発生
手段10aおよび摩擦クラッチ10bを備えている。Thus, the driving force transmission device 10 is provided with a pressing force generating means 10a and a friction clutch 10b in an annular working chamber composed of the outer case 11 and the inner shaft 12.
アウタケース11は所定長さの筒部11aの一端に内向フ
ランジ部11bを備えてなり、筒部11aの他端が開口してい
て開口端部である他端側内周にネジ部11cが形成されて
いる。インナシャフト12は所定長さの段付きの筒部12a
の中間部外周に外向フランジ部12bを備えてなり、フラ
ンジ部12bの外周には軸方向へ延びる外スプライン部12c
が形成され、かつ筒部12aの一端側内周には軸方向へ延
びる内スプライン部12dが形成されている。かかるイン
ナシャフト12においては、その筒部12aの一端がアウタ
ケース11の内向フランジ部11bの内孔内に液密的かつ回
転可能に嵌合されていて、筒部12aの他端側外周に組付
けた後述の押圧力発生手段10aの構成部材を介してアウ
タケース11に回転可能に支持されている。インナシャフ
ト12はその内スプライン部12dにて第２プロペラシャフ
ト26の先端部のスプライン26aに嵌合して固定され、か
つアウタケース11は第１プロペラシャフト25の後端に固
定されている。The outer case 11 is provided with an inward flange portion 11b at one end of a tubular portion 11a having a predetermined length, the other end of the tubular portion 11a is open, and a screw portion 11c is formed on the inner circumference of the other end, which is the open end. Has been done. The inner shaft 12 is a cylindrical portion 12a with a step of a predetermined length.
The outer periphery of the middle portion of the outer peripheral surface of the flange portion 12b is provided with an outward flange portion 12b.
Is formed, and an inner spline portion 12d extending in the axial direction is formed on the inner circumference of the one end side of the cylindrical portion 12a. In the inner shaft 12, one end of the tubular portion 12a is fitted in the inner hole of the inward flange portion 11b of the outer case 11 in a liquid-tight and rotatable manner, and is assembled to the outer periphery of the other end of the tubular portion 12a. It is rotatably supported by the outer case 11 via the constituent members of the attached pressing force generating means 10a described later. The inner shaft 12 is fitted and fixed to the spline 26a at the tip of the second propeller shaft 26 at the inner spline portion 12d, and the outer case 11 is fixed to the rear end of the first propeller shaft 25.
押圧力発生手段10aは作動ピストン13、ロータ14およ
びリテーナ15からなり、かつ摩擦クラッチ10bは湿式多
板クラッチ式のもので、多数のクラッチプレート16およ
びクラッチディスク17からなる。各クラッチプレート16
はその外周のスプライン部をアウタケース11の内周に設
けたスプライン部11dに嵌合されて、同ケース11に一体
回転可能かつ軸方向へ移動可能に組付けられている。各
クラッチディスク17はその内周のスプライン部をインナ
シャフト12の外スプランイ部12cに嵌合されて各クラッ
チプレート16間に位置し、同シャフト12に一体回転可能
かつ軸方向へ移動可能に組付けられている。これらのク
ラッチプレート16およびクラッチディスク17の収容室R1
にはクラッチ用オイルと気体とが所定量封入されてい
る。The pressing force generating means 10a comprises an operating piston 13, a rotor 14 and a retainer 15, and the friction clutch 10b is of a wet multi-plate clutch type and comprises a large number of clutch plates 16 and clutch discs 17. Each clutch plate 16
The outer peripheral spline portion is fitted to the spline portion 11d provided on the inner periphery of the outer case 11, and is assembled to the case 11 so as to be integrally rotatable and movable in the axial direction. Each clutch disc 17 has its inner peripheral spline portion fitted to the outer splint portion 12c of the inner shaft 12 so as to be located between the clutch plates 16 and assembled to the shaft 12 so as to be integrally rotatable and movable in the axial direction. Has been. Storage chamber R1 for these clutch plate 16 and clutch disc 17
A predetermined amount of clutch oil and gas is enclosed in the.
押圧力発生手段10aを構成する作動ピストン13はアウ
タケース11の筒部11aの他端側内周に液密的に一体回転
可能かつ軸方向へ摺動可能に、またインナシャフト12に
対してはその外周に液密的に回転可能かつ軸方向へ摺動
可能にそれぞれ組付けられていて、その一側面13aにて
図示最右端のクラッチプレート16に対向して当接してい
る。ロータ14は第１図および第２図に示すように、環状
ボス部14aの外周の互に180°離れた部位にて半径方向へ
延びる２枚のベーン部14bを備えてなり、環状ボス部14a
にてインナシャフト12の筒部12a外周に一体的に組付け
られている。かかるロータ14は作動ピストン13の他側に
設けた環状凹所13bの深さと略同じ厚みに形成されてい
て、環状凹所13b内に嵌合している。しかして、リテー
ナ15はその他端側外周にネジ部15aを備え、インナシャ
フト12の筒部12aの他端側外周に液密的に軸方向へ摺動
可能かつ回転可能に嵌合され、アウタケース11に対して
はそのネジ部15aをアウタケース11のネジ部11cに進退可
能に螺着され、かつ液密的となっている。かかるリテー
ナ15においては、軸方向の位置調整がなされてアウタケ
ース11の他端にスポット溶接にて結合され、その一側面
15bにて作動ピストン13の他側の環状外縁面13cに当接
し、その一側面15bと作動ピストン13の環状凹所13bとに
よりロータ14が位置する流体室を形成しているととも
に、作動ピストン13を介して摩擦クラッチ10bのプレロ
ードを調整している。なお、スポット溶接は互に180°
離れた２箇所でなされている。なお、溶接部位は符号15
cにて示されている。この流体室内にはシリコンオイル
等高粘性流体が所定量封入されており、またロータ14は
そのベーン部14bの外周を環状凹所13bの内周に液密的に
接触させ、かつベーン部14bの両側面と環状凹所13bの他
側面13b1およびリテーナ15の一側面15b間に微小間隙を
形成して、流体室内を２つの滞留室R2に区画している。The working piston 13 forming the pressing force generating means 10a is liquid-tightly integrally rotatable with the inner circumference of the other end side of the tubular portion 11a of the outer case 11 and slidable in the axial direction. Liquid-tightly rotatably and axially slidably assembled to the outer circumference of the outer peripheral surface, and one side surface 13a of the outer peripheral surface abuts against the rightmost clutch plate 16 in the figure. As shown in FIGS. 1 and 2, the rotor 14 is provided with two vane portions 14b extending in the radial direction at portions of the outer circumference of the annular boss portion 14a that are separated from each other by 180 °.
Are integrally assembled to the outer circumference of the cylindrical portion 12a of the inner shaft 12. The rotor 14 is formed to have substantially the same thickness as the depth of the annular recess 13b provided on the other side of the working piston 13, and is fitted in the annular recess 13b. Thus, the retainer 15 is provided with a threaded portion 15a on the outer periphery on the other end side, is fitted to the outer periphery on the other end side of the tubular portion 12a of the inner shaft 12 in a liquid-tight manner so as to be slidable and rotatable in the axial direction, and the outer case The screw portion 15a of 11 is screwed to the screw portion 11c of the outer case 11 so as to be able to move forward and backward, and is liquid-tight. In the retainer 15, the position of the retainer 15 is adjusted in the axial direction, and the retainer 15 is joined to the other end of the outer case 11 by spot welding.
15b is in contact with the annular outer edge surface 13c on the other side of the working piston 13, and one side surface 15b and the annular recess 13b of the working piston 13 form a fluid chamber in which the rotor 14 is located. The preload of the friction clutch 10b is adjusted via. In addition, spot welding is 180 ° to each other
It is done in two separate locations. Note that the welded part is symbol 15
indicated by c. A predetermined amount of highly viscous fluid such as silicon oil is enclosed in this fluid chamber, and the rotor 14 makes the outer periphery of its vane portion 14b liquid-tightly contact the inner periphery of the annular recess 13b, and A minute gap is formed between both side surfaces and the other side surface 13b1 of the annular recess 13b and one side surface 15b of the retainer 15 to divide the fluid chamber into two retention chambers R2.
かかる構成の駆動力伝達装置10においては、第１、第
２両プロペラシャフト25、26間に相対回転が生じるとト
ルク伝達がなされる。すなわち、これら両シャフト25、
26間に相対回転が生じると、第１プロペラシャフト25に
一体回転可能に組付けられているアウタケース11、作動
ピストン13およびリテーナ15と、第２プロペラシャフト
26に一体回転可能に組付けられているインナシャフト12
およびロータ14との間に相対回転が生じる。従って、押
圧力発生手段10aの流体室内においては、滞留室R2内の
粘性流体が相対回転数に比例した速度にて強制的に流動
させられ、周方向に順次相対移行する滞留室R2内では流
動抵抗に起因してベーン部14bの下流側端から次のベー
ン部14bの上流側端に向って漸次増圧される圧力分布が
発生する。この圧力分布の増圧部分は差動回転数に比例
して増大するもので、作動ピストン13を軸方向へ押圧す
る。この結果、作動ピストン13は摩擦クラッチ10bを押
圧して摩擦クラッチ10bを構成する各クラッチプレート1
6とクラッチディスク17をクラッチ用オイルを介して摩
擦係合させる。これにより、摩擦クラッチ10bにおいて
は差動回転数に比例したトルクをアウタケース11からイ
ンナシャフト12に伝達し、車両は４輪駆動状態となる。
また、この４輪駆動状態においては前後輪の差動回転を
許容し、タイトコーナブレーキング現象の発生も防止さ
れる。In the driving force transmission device 10 having such a configuration, torque is transmitted when relative rotation occurs between the first and second propeller shafts 25 and 26. That is, these both shafts 25,
When a relative rotation occurs between the first and second propeller shafts 25, the outer case 11, the working piston 13 and the retainer 15 that are integrally rotatably assembled to the first propeller shaft 25, and the second propeller shaft
Inner shaft 12 that is integrally rotatable with 26
And relative rotation occurs between the rotor 14 and the rotor 14. Therefore, in the fluid chamber of the pressing force generating means 10a, the viscous fluid in the retention chamber R2 is forcibly flown at a speed proportional to the relative rotation speed, and flows in the retention chamber R2 that sequentially shifts in the circumferential direction. Due to the resistance, a pressure distribution in which the pressure is gradually increased from the downstream end of the vane portion 14b toward the upstream end of the next vane portion 14b is generated. The pressure increasing portion of this pressure distribution increases in proportion to the differential rotation speed, and presses the working piston 13 in the axial direction. As a result, the working piston 13 presses the friction clutch 10b and each clutch plate 1 that constitutes the friction clutch 10b.
6 and the clutch disc 17 are frictionally engaged with each other via the clutch oil. As a result, in the friction clutch 10b, torque proportional to the differential rotation speed is transmitted from the outer case 11 to the inner shaft 12, and the vehicle is in the four-wheel drive state.
Further, in this four-wheel drive state, differential rotation of the front and rear wheels is allowed, and the occurrence of the tight corner braking phenomenon is prevented.
ところで、当該駆動力伝達装置10においては組付作業
においてリテーナ15をアウタケース11に螺着して進退さ
せることにより、ロータ14の両側面と作動ピストン13、
リテーナ15の各側面との微小間隙、摩擦クラッチ10bの
クラッチプレート16とクラッチディスク17間の微小間
隙、摩擦クラッチ10bに対するプレロードを精度よく設
定することができる。By the way, in the driving force transmission device 10, by assembling the retainer 15 to the outer case 11 to advance and retreat in the assembling work, both side surfaces of the rotor 14 and the working piston 13,
It is possible to accurately set the minute gap between each side surface of the retainer 15, the minute gap between the clutch plate 16 and the clutch disc 17 of the friction clutch 10b, and the preload for the friction clutch 10b.
特に、当該駆動力伝達装置10においては、リテーナ15
をアウタケース11の開口端部に螺着して作動ピストン13
の環状外縁面13cに当接させて、作動ピストン13の環状
凹所13bとリテーナ15間に流体室を形成するとともに作
動ピストン13を介して摩擦クラッチ10bのプレロードを
調整しているので、リテーナ15からロータ14を介するこ
となく直接作動ピストン13に押圧力が伝達され、押圧力
発生手段10aにおける圧力特性に影響を及ぼすことな
く、摩擦クラッチ10bのプレロードを精度よく調整して
設定することができる。Particularly, in the driving force transmission device 10, the retainer 15
Is screwed onto the open end of the outer case 11 and the working piston 13
Since the fluid chamber is formed between the annular recess 13b of the operating piston 13 and the retainer 15 by contacting the annular outer edge surface 13c of the retainer 15, the preload of the friction clutch 10b is adjusted via the operating piston 13, the retainer 15 From here, the pressing force is directly transmitted to the working piston 13 without passing through the rotor 14, and the preload of the friction clutch 10b can be accurately adjusted and set without affecting the pressure characteristics in the pressing force generating means 10a.
また、これらの設定後リテーナ15わアウタケース11に
スポット溶接にて結合することにより、リテーナ15はア
ウタケース11に対して正確に位置決めされ、かつその後
リテーナ15が緩んで上記微小間隙、プレロードが変動す
るおそれは全くない。この場合、組付用の特別の部材は
全く不要であり、またアウタケース11とリテーナ15との
結合にカシメ手段を用いる場合のごとくこれら両者11、
15に亀裂が生じるおそれも全くない。Also, after these settings, the retainer 15 is accurately positioned with respect to the outer case 11 by connecting it to the outer case 11 by spot welding, and then the retainer 15 loosens and the minute gap and preload change. There is no danger of doing so. In this case, no special member for assembly is necessary, and both of these 11, as in the case of using the caulking means for connecting the outer case 11 and the retainer 15,
There is no risk of cracking at 15.
第１図は本考案の一実施例に係る駆動力伝達装置の断面
図、第２図は第１図の矢印II-II線方向の断面図、第３
図は同装置を採用した車両の概略図である。 符号の説明 10……駆動力伝達装置、10a……押圧力発生手段、10b…
…摩擦クラッチ、11……アウタケース、12……インナシ
ャフト、13……作動ピストン、14……ロータ、14b……
ベーン部、15……リテーナ、15c……スポット溶接部、1
6……クラッチプレート、17……クラッチディスク、25,
26……プロペラシャフト。FIG. 1 is a sectional view of a driving force transmission device according to an embodiment of the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG.
The figure is a schematic diagram of a vehicle that employs the same device. Explanation of reference numerals 10 ... Driving force transmitting device, 10a ... Pressing force generating means, 10b ...
Friction clutch, 11 outer case, 12 inner shaft, 13 working piston, 14 rotor, 14b
Vane, 15 …… Retainer, 15c …… Spot weld, 1
6 …… Clutch plate, 17 …… Clutch disc, 25,
26 …… Propeller shaft.
───────────────────────────────────────────────────── フロントページの続き (72)考案者 林 保明 愛知県刈谷市朝日町１丁目１番地 豊田 工機株式会社内 (72)考案者 宅野 博 愛知県刈谷市朝日町１丁目１番地 豊田 工機株式会社内 (56)参考文献 特開 昭63−240429（ＪＰ，Ａ) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yasuaki Hayashi 1-1 Asahi-cho, Kariya City, Aichi Toyota Koki Co., Ltd. Incorporated (56) References JP-A-63-240429 (JP, A)
Claims (1)
回転部材間に配設され、これら両回転部材の相対回転に
より作動して両回転部材をトルク伝達可能に連結する摩
擦係合力を発生させるとともに付与される軸方向の押圧
力に応じて前記摩擦係合力を増減させる摩擦クラッチ、
および前記両回転部材の相対回転に応じた軸方向の押圧
力を発生させて前記摩擦クラッチに付与する押圧力発生
手段を備え、同押圧力発生手段を、前記両回転部材間に
液密的に軸方向へ摺動可能かつ外側回転部材に一体回転
可能に組付けられて一側を前記摩擦クラッチに当接する
作動ピストンと、前記外側回転部材の開口端部に一体回
転可能に設けられて前記作動ピストンの他側との間に軸
方向に所定間隔を有して粘性流体が封入される流体室を
形成するリテーナと、半径方向へ延びる１または複数の
ベーン部を備え前記流体室にて前記内側回転部材に一体
回転可能に組付けられたロータとにより構成してなる駆
動力伝達装置において、前記作動ピストンの他側に環状
凹所を形成し、かつ前記外側回転部材の開口端部の内周
にネジ部を設けるとともに前記リテーナの外端部の外周
に前記ネジ部に進退可能に螺着されるネジ部を設け、前
記リテーナを前記外側回転部材に螺着して前記作動ピス
トンの環状外縁面に当接させて、同作動ピストンの他側
にて前記環状凹所と前記リテーナ間に前記流体室を形成
するとともに前記作動ピストンを介して前記摩擦クラッ
チのプレロードを調整し、その後前記外側回転部材と前
記リテーナをスポット溶接にて互いに結合したことを特
徴とする駆動力伝達装置。1. A frictional engagement force which is disposed between both inner and outer rotating members coaxially and relatively rotatably arranged and which is actuated by relative rotation of these both rotating members to couple the both rotating members so that torque can be transmitted. And a friction clutch that increases or decreases the friction engagement force according to the axial pressing force applied,
And a pressing force generating means for generating an axial pressing force corresponding to the relative rotation of the rotating members and applying the pressing force to the friction clutch, the pressing force generating means being liquid-tight between the rotating members. An operating piston that is slidable in the axial direction and is integrally rotatably mounted on the outer rotating member and has one side in contact with the friction clutch; and an operating piston that is integrally rotatably provided at an opening end of the outer rotating member. A retainer that forms a fluid chamber in which a viscous fluid is enclosed with a predetermined distance in the axial direction from the other side of the piston, and one or a plurality of vane portions that extend in the radial direction are provided. In a driving force transmission device configured by a rotor integrally rotatably mounted on a rotating member, an annular recess is formed on the other side of the working piston, and an inner circumference of an opening end of the outer rotating member is formed. Provide a screw part on A screw portion is provided on the outer periphery of the outer end portion of the retainer, which is screwed so as to be capable of advancing and retreating with the screw portion, and the retainer is screwed to the outer rotating member so as to abut the annular outer edge surface of the working piston. , Forming the fluid chamber between the annular recess and the retainer on the other side of the operating piston and adjusting the preload of the friction clutch via the operating piston, and then spotting the outer rotating member and the retainer. A driving force transmission device characterized by being connected to each other by welding.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989092819U JP2508957Y2 (en) | 1989-08-07 | 1989-08-07 | Driving force transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989092819U JP2508957Y2 (en) | 1989-08-07 | 1989-08-07 | Driving force transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0332222U JPH0332222U (en) | 1991-03-28 |
| JP2508957Y2 true JP2508957Y2 (en) | 1996-08-28 |
Family
ID=31642230
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1989092819U Expired - Fee Related JP2508957Y2 (en) | 1989-08-07 | 1989-08-07 | Driving force transmission device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2508957Y2 (en) |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0717162B2 (en) * | 1987-03-27 | 1995-03-01 | 豊田工機株式会社 | Torque transmission device |
-
1989
- 1989-08-07 JP JP1989092819U patent/JP2508957Y2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0332222U (en) | 1991-03-28 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |