JPH0999755A - Motive power transmitting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To disconnect a front wheel driving system at two-wheel drive traveling time, and select an overrunning mode of front wheels and a traveling mode in a directly connected condition of four wheels at four-wheel drive traveling time by arranging a pair of meshing parts joined so as to be freely disconnected in a case of a lock means and a driven member. SOLUTION: Since a holder 23 of an engaging piece 32 of a two-way clutch (a) is made joinable so as to be freely disconnected by a driven member 16, free running of the clutch (a) can be optionally stopped. A torque transmitting passage can be changed to an opening condition and a directly connected condition between a driving member 18 and the driven member 16, and two-wheel drive travel can be performed in a condition where a longitudinal driving system is disconnected, and since a friction type rotation transmitting mechanism 42 is arranged in a lock mechanism 38, an overrunning mode of front wheels 2 and a lock mode of directly connecting front and rear wheels can be selected at four-wheel drive traveling time. Four-wheel drive travel which can precisely cope with a change in a road surface, can be realized even at overrunning mode time.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】この発明は、４輪駆動車のディフ
ァレンシャルと車輪間の駆動経路上において、駆動力の
伝達と遮断を切換える動力伝達装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device for switching between transmission and interruption of driving force on a drive path between a differential and wheels of a four-wheel drive vehicle.

【０００２】[0002]

【従来の技術】パートタイム式の４輪駆動車には、後車
輪を常時駆動すると共に、前車輪の車軸とホイールハブ
との間にハブクラッチ装置を組込み、そのハブクラッチ
装置によりホイールハブへの駆動力の伝達と遮断を行な
って、４輪駆動と２輪駆動を切換えるようにしたものが
ある。2. Description of the Related Art In a part-time four-wheel drive vehicle, the rear wheels are always driven, and a hub clutch device is incorporated between the axle of the front wheels and the wheel hub. There is one that switches between four-wheel drive and two-wheel drive by transmitting and blocking the driving force.

【０００３】従来のハブクラッチ装置には、駆動の切換
え方法として手動式と自動式のものがあるが、いずれも
車軸とホイールハブを単に結合するか、切り離す機能し
かもたされていない。Conventional hub clutch devices include manual and automatic drive switching methods, but both have only the function of simply connecting or disconnecting the axle and the wheel hub.

【０００４】[0004]

【発明が解決しようとする課題】すなわち、従来のハブ
クラッチ装置は、車軸の動きに連動するカム機構等の作
用によって車軸に嵌合したスライドギヤを移動させ、そ
のスライドギヤをホイールハブに噛み合せて、車軸とホ
イールハブを断接するようにしているが、ハブクラッチ
装置が係合した時は、車軸とホイールハブが直結した４
輪駆動状態になるため、その状態でタイトコーナ等を旋
回した際、前車輪と後車輪の間に生じる旋回距離の差に
よってタイトコーナブレーキ現象を起こし、前後輪間に
スリップが生じ、未舗装道路や滑りやすい道路でしか走
行できない。That is, in the conventional hub clutch device, the slide gear fitted to the axle is moved by the action of the cam mechanism or the like that interlocks with the movement of the axle, and the slide gear is meshed with the wheel hub. , The axle and the wheel hub are connected and disconnected, but when the hub clutch device is engaged, the axle and the wheel hub are directly connected.
Since the vehicle is in a wheel drive state, when a tight corner or the like is turned in that state, a tight corner braking phenomenon occurs due to the difference in the turning distance between the front wheel and the rear wheel, slipping occurs between the front and rear wheels, and it may occur on unpaved roads. You can only drive on slippery roads.

【０００５】このため、舗装道路等を走行する場合は、
運転者がその都度ハブクラッチ装置の係合を切換えて前
後輪間の連結を切離す必要があり、その駆動の切換え操
作に手間がかかる問題があった。Therefore, when traveling on a paved road or the like,
Each time the driver needs to switch the engagement of the hub clutch device to disconnect the front and rear wheels from each other, there is a problem that the drive switching operation is troublesome.

【０００６】また、車軸とホイールハブの間にハブクラ
ッチ装置を組込んだ構造は、車両の組立て工程におい
て、ディファレンシャルとハブクラッチ装置が別部品と
なり、車両の組立て作業に手間と時間がかかるという問
題がある。Further, in the structure in which the hub clutch device is incorporated between the axle and the wheel hub, the differential and the hub clutch device are separate parts in the vehicle assembling process, and it takes a lot of time and effort to assemble the vehicle. There is.

【０００７】そこで、この発明の課題は、２駆走行時は
前輪駆動系を切離し、４駆走行時には前車輪のオーバラ
ンニングモードと４輪の直結状態の走行モードを選択す
ることができ、タイトコーナブレーキ現象の発生がな
く、しかもディファレンシャルとのユニット化によって
車両組立ての能率向上を図ることができる車両の駆動力
伝達装置を提供することにある。Therefore, the object of the present invention is to separate the front wheel drive system during two-wheel drive and to select the front-wheel overrunning mode and the four-wheel direct drive mode during four-wheel drive. It is an object of the present invention to provide a driving force transmission device for a vehicle that does not generate a braking phenomenon and that can improve the efficiency of vehicle assembly by forming a unit with a differential.

【０００８】[0008]

【課題を解決するための手段】上記のような課題を解決
するため、請求項１の発明は、入力軸に固定した駆動部
材と出力軸に固定した従動部材の間に、複数の係合子
と、各係合子を駆動部材と従動部材に対する係合作動位
置に移動させるための保持器からなる二方向クラッチを
組込み、前記入力軸に外部からの遠隔操作により保持器
と従動部材を切離し自在に結合するロック手段を設け、
このロック手段が、入力軸と一体に回転し、軸方向に移
動自在となるスライダーと、スライダーの外側に位置す
るケースと、スライダーの回転を摩擦力でケースに伝達
する回転伝達機構とで形成され、このロック手段のケー
スと前記従動部材とに、切離し自在に結合する一対の噛
合い部を設けた構成を採用したものである。In order to solve the above problems, the invention according to claim 1 provides a plurality of engaging elements between a driving member fixed to an input shaft and a driven member fixed to an output shaft. , A two-way clutch composed of a retainer for moving each of the engaging elements to an engagement operating position with respect to the driving member and the driven member, and the retainer and the driven member are detachably coupled to the input shaft by a remote operation from the outside. Locking means to
This locking means is formed by a slider that rotates integrally with the input shaft and is movable in the axial direction, a case located outside the slider, and a rotation transmission mechanism that transmits the rotation of the slider to the case by frictional force. The case of the locking means and the driven member are provided with a pair of meshing portions that are detachably coupled to each other.

【０００９】請求項２の発明は、上記ロック手段を、入
力軸に軸方向への移動が自在となるよう嵌挿したスライ
ダーと、保持器と従動部材の一方に係合しつつ他方に設
けた噛合い部に対して接近離反する結合部材を軸方向に
一体動するよう結合し、スライダーに連結した操作用フ
ォークで該スライダーを軸方向に移動させるようにした
構成としたものである。According to a second aspect of the present invention, the locking means is provided on the other side while engaging with the slider fitted to the input shaft so as to be movable in the axial direction and one of the retainer and the driven member. A connecting member that moves toward and away from the meshing portion is connected so as to integrally move in the axial direction, and the slider is moved in the axial direction by an operating fork connected to the slider.

【００１０】[0010]

【発明の実施の形態】以下、この発明の実施の形態を図
示例と共に説明する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

【００１１】図１は、後輪駆動を主とする４輪駆動車の
車輪駆動系を示したものであり、同図において、１はフ
ロンドディファレンシャル、２は前車輪、３は後車輪を
示している。FIG. 1 shows a wheel drive system of a four-wheel drive vehicle mainly for rear wheel drive. In FIG. 1, 1 is a front differential, 2 is a front wheel, and 3 is a rear wheel. There is.

【００１２】フロントディファレンシャル１は、デフカ
バー４の内部に、リングギヤ５とドライブピニオン６を
介してエンジン７とトランスファー８に連結されるデフ
ケース９を回転自在に支持し、そのデフケース９と共回
り可能に連結したピニオンギヤ１０、１０に一対のサイ
ドギヤ１１、１１を噛み合せて構成され、この各サイド
ギヤ１１、１１に、駆動軸としての車軸１２、１３が連
結されている。The front differential 1 rotatably supports a differential case 9 which is connected to an engine 7 and a transfer 8 via a ring gear 5 and a drive pinion 6 inside a differential cover 4, and is rotatably connected to the differential case 9. The pinion gears 10 and 10 are configured to mesh with a pair of side gears 11 and 11. The side gears 11 and 11 are connected to axles 12 and 13 as drive shafts.

【００１３】図１と図２の如く、上記車軸１２、１３の
うち、短尺側の車軸１３は、等速ジョイント１４を介し
て前車輪２に連結されている。As shown in FIGS. 1 and 2, of the axles 12 and 13, the shorter axle 13 is connected to the front wheel 2 via a constant velocity joint 14.

【００１４】一方、長尺側の車軸１２は、その車軸１２
が挿通するデフカバー４の内部において、途中で駆動軸
１２ａと１２ｂに軸方向に同軸心状の配置となるよう２
つに分離され、この分離部分に動力伝達装置Ａがデフカ
バー４内に納まる状態で組込まれ、外側の駆動軸１２ｂ
は等速ジョイント１４を介して前車輪２に連結されてい
る。On the other hand, the long axle 12 has the axle 12
Inside the differential cover 4 through which the shaft is inserted so that the drive shafts 12a and 12b are coaxially arranged axially in the middle.
And the power transmission device A is installed in the separated portion so as to be housed inside the differential cover 4, and the outer drive shaft 12b
Is connected to the front wheel 2 via a constant velocity joint 14.

【００１５】図２乃至図５は、動力伝達装置Ａの例を示
し、分離された車輪側の駆動軸１２ｂ（従動軸）にスプ
ライン１５を介して従動部材となる外輪１６を連結し、
ディファレンシャル側の駆動軸１２ａ（入力軸）にスプ
ライン１７を介して駆動部材となる内輪１８を連結し、
上記外輪１６を軸受１９とスリーブ２０を用いてデフカ
バー４で回動自在に支持し、この外輪１６の内部に内輪
１８が回転自在に嵌り合っている。2 to 5 show an example of the power transmission device A, in which an outer ring 16 which is a driven member is connected to a separated wheel side drive shaft 12b (driven shaft) via a spline 15.
An inner ring 18, which is a drive member, is connected to a drive shaft 12a (input shaft) on the differential side via a spline 17.
The outer ring 16 is rotatably supported by the differential cover 4 using a bearing 19 and a sleeve 20, and an inner ring 18 is rotatably fitted inside the outer ring 16.

【００１６】上記外輪１６の内径面と内輪１８の外径面
には、図７及び図９に示すように、同芯の円筒面２１、
２２が形成され、その両円筒面２１、２２の間に大径保
持器２３と小径保持器２４が組込まれている。As shown in FIGS. 7 and 9, the inner diameter surface of the outer ring 16 and the outer diameter surface of the inner ring 18 are concentric cylindrical surfaces 21,
22 is formed, and a large-diameter cage 23 and a small-diameter cage 24 are incorporated between the two cylindrical surfaces 21, 22.

【００１７】上記大径保持器２３は、図３に示すよう
に、後端部に延長腕２５が一体に形成され、その延長腕
２５が軸受２６の案内により外輪１６と内輪１８に対し
て回転自在に支持されている。As shown in FIG. 3, the large-diameter cage 23 has an extension arm 25 integrally formed at a rear end thereof, and the extension arm 25 is rotated with respect to the outer ring 16 and the inner ring 18 by the guide of a bearing 26. It is supported freely.

【００１８】一方、小径保持器２４は、前端部に、内径
側に向かって屈曲する屈曲部２７が形成され、その屈曲
部２７が内輪１８の端面にすべり回転可能に接触してお
り、この屈曲部２７と止め輪２８との間に、皿バネから
成る圧着バネ２９が組込まれている。この圧着バネ２９
は、屈曲部２７を内輪１８の端面に向かって圧着してお
り、その押圧力によって生じる摩擦力により小径保持器
２４を内輪１８に圧着している。On the other hand, the small-diameter cage 24 has a bent portion 27 which is bent toward the inner diameter side at the front end thereof, and the bent portion 27 is in sliding contact with the end surface of the inner ring 18 so as to be rotatable. A crimp spring 29, which is a disc spring, is incorporated between the portion 27 and the retaining ring 28. This crimp spring 29
, The bending portion 27 is crimped toward the end surface of the inner ring 18, and the small diameter cage 24 is crimped to the inner ring 18 by the frictional force generated by the pressing force.

【００１９】また、上記大径保持器２３と小径保持器２
４の周面には、図７及び図９に示すように、径方向に対
向して複数のポケット３０、３１が形成され、その各ポ
ケット３０、３１に、係合子としてのスプラグ３２と、
スプラグ３２を保持するバネ３３とが組込まれている。The large diameter cage 23 and the small diameter cage 2 are also provided.
As shown in FIGS. 7 and 9, a plurality of pockets 30 and 31 are formed in the circumferential surface of the No. 4 so as to face each other in the radial direction, and a sprag 32 as an engaging element is provided in each of the pockets 30 and 31.
A spring 33 that holds the sprag 32 is incorporated.

【００２０】このスプラグ３２は、外径側と内径側に、
それぞれ異なった曲率中心をもつ左右対称形の円弧面３
４と３４ａが形成され、左右の両方向に所定角度傾くと
両円筒面２１、２２と係合し、外輪１６と内輪１８を一
体化する。また、バネ３３は、大径保持器３３に一端が
支持されてスプラグ３２を両側から押圧し、各スプラグ
３２を円筒面２１、２２と係合しない位置に保持してい
る。従って、大径保持器２３と小径保持器２４及びスプ
ラグ３２によって二方向クラッチａを形成している。The sprag 32 has an outer diameter side and an inner diameter side.
Left and right symmetrical arc surface 3 with different centers of curvature
4 and 34a are formed, and when they are inclined at a predetermined angle in both left and right directions, they engage with both cylindrical surfaces 21 and 22, and the outer ring 16 and the inner ring 18 are integrated. The spring 33 has one end supported by the large-diameter retainer 33 and presses the sprags 32 from both sides, and holds the sprags 32 at positions where they do not engage with the cylindrical surfaces 21 and 22. Therefore, the large diameter cage 23, the small diameter cage 24, and the sprag 32 form a two-way clutch a.

【００２１】また、上記大径保持器２３及び小径保持器
２４の端部には、図８に示すように、それぞれ径方向に
貫通するスリット３５、３６が形成され、そのスリット
３５、３６に、Ｃ字形のリング形状をしたスイッチバネ
３７の両端部が係合している。このスイッチバネ３７
は、周方向に縮められた状態でセットされ、一端を大径
保持器２３に、他端を小径保持器２４に押し付けて取付
けられており、そのバネ力によって両保持器２３、２４
に円周方向の力を与えている。この力により大径保持器
２３は回転力を受け、上記スイッチバネ３７のバネ力に
より、両保持器２３、２４とスプラグ３２は、回転の一
方向の噛み合い位置でスタンバイの状態となっている。
上記の構造では、スイッチバネ３７が大径保持器２３に
一方向の回転力を付与する手段を構成する。Further, as shown in FIG. 8, slits 35, 36 penetrating in the radial direction are formed at the ends of the large-diameter cage 23 and the small-diameter cage 24, respectively. Both ends of a C-shaped ring-shaped switch spring 37 are engaged with each other. This switch spring 37
Are set in a state of being contracted in the circumferential direction, one end of which is attached to the large diameter retainer 23 and the other end of which is pressed against the small diameter retainer 24. The spring force of both retainers 23, 24
To give a circumferential force to. This force causes the large-diameter retainer 23 to receive a rotational force, and the spring force of the switch spring 37 causes the retainers 23 and 24 and the sprag 32 to be in a standby state at a meshing position in one direction of rotation.
In the above structure, the switch spring 37 constitutes a means for applying a unidirectional rotational force to the large diameter cage 23.

【００２２】前記駆動軸１２ａには、大径保持器２３の
延長腕２５の後端側の位置にロック手段３８が外部から
の操作で軸方向に移動するように設けられている。A lock means 38 is provided on the drive shaft 12a at a position on the rear end side of the extension arm 25 of the large diameter cage 23 so as to be axially moved by an external operation.

【００２３】このロック手段３８は、図２乃至図５の如
く、駆動軸１２ａに軸方向への移動が自在で駆動軸１２
ａと回転方向に一体となるようスプライン結合した円筒
状のスライダー３９と、このスライダー３９の先端に外
嵌状となるよう固定した環状の結合部材４０と、スライ
ダー３９の外側に外嵌するよう配置した環状の多板ケー
ス４１と、スライダ３９とケース４１の間に組込まれ、
スライダー３９の回転を摩擦力でケース４１に伝達する
回転伝達機構４２とで形成され、このロック手段３８に
対応するため、外輪１６の内径面に、スプライン状の歯
形を内周に形成した環状の噛合い部材４３が圧入固定さ
れ、大径保持器２３の延長腕２５の端部には、複数の切
欠き４４が設けられている。As shown in FIGS. 2 to 5, the locking means 38 is movable in the axial direction of the drive shaft 12a and is freely movable.
a cylindrical slider 39 that is spline-coupled so as to be integrated with a in the rotation direction, an annular coupling member 40 that is fixed to the tip of this slider 39 so as to be externally fitted, and is arranged so as to be externally fitted to the outside of the slider 39. The annular multi-plate case 41, which is assembled between the slider 39 and the case 41,
It is formed by a rotation transmission mechanism 42 that transmits the rotation of the slider 39 to the case 41 by a frictional force, and in order to correspond to this locking means 38, an annular shape in which a spline tooth profile is formed on the inner periphery of the inner surface of the outer ring 16. The engagement member 43 is press-fitted and fixed, and a plurality of notches 44 are provided at the end of the extension arm 25 of the large diameter cage 23.

【００２４】上記結合部材４０は、図６のように、外周
に軸方向前方へ屈曲するよう設けた複数の突起４５が大
径保持器２３の延長部２５に設けた溝４４に嵌合してお
り、この突起４５と溝４４の案内により大径保持器２３
と共回り状態で軸方向にスライドする。As shown in FIG. 6, the coupling member 40 has a plurality of protrusions 45 formed on its outer periphery so as to be bent forward in the axial direction, and are fitted into the grooves 44 formed in the extension portion 25 of the large diameter cage 23. The large diameter cage 23 is guided by the projection 45 and the groove 44.
Slide in the axial direction while rotating with.

【００２５】上記結合部材４０の外周に半径方向の外方
へ突出する複数の突起４６が設けられ、図５の如く、ス
ライダー３９を内輪１８に最も接近する前進位置にする
と、該突起４６は噛合い部材４３の歯形凹部４７と噛合
い、これにより、大径保持器２３と外輪１６を回転方向
に結合一体化する。A plurality of projections 46 projecting outward in the radial direction are provided on the outer periphery of the coupling member 40, and when the slider 39 is at the forward position closest to the inner ring 18 as shown in FIG. 5, the projections 46 mesh with each other. It meshes with the tooth-shaped recess 47 of the first member 43, whereby the large-diameter retainer 23 and the outer ring 16 are coupled and integrated in the rotational direction.

【００２６】また、図３の如く、スライダー３９を内輪
１８に対して離反する後退位置に移動させると、結合部
材４０の突起４６は噛合い部材４３から離反し、突起４
６は歯形凹部４７から離脱し、大径保持器２３と外輪１
６の回転方向の結合を解くことになる。As shown in FIG. 3, when the slider 39 is moved to the retracted position away from the inner ring 18, the projection 46 of the coupling member 40 separates from the meshing member 43, and the projection 4
6 is disengaged from the tooth-shaped recess 47, and the large diameter cage 23 and the outer ring 1
6 will be uncoupled in the direction of rotation.

【００２７】前記スライダー３９には後端に設けた溝４
８に操作用フォーク４９が係合している。この操作用フ
ォーク４９は、図１のように車両のトランスファー８に
接続するアクチェータ等と連結しており、トランスファ
ー８からの遠隔操作によりスライダ３９を軸方向に移動
させ、結合部材４０を噛合い部材４３に対して接近離反
させるようになっている。The slider 39 has a groove 4 at the rear end.
The operation fork 49 is engaged with the shaft 8. The operation fork 49 is connected to an actuator or the like connected to the transfer 8 of the vehicle as shown in FIG. 1, and the slider 39 is moved in the axial direction by a remote operation from the transfer 8 so that the coupling member 40 is engaged with the engaging member. It is made to approach and separate from 43.

【００２８】前記多板ケース４１は外輪１６と略等しい
外径を有する断面Ｌ字形の環状に形成され、前面が結合
部材４０の後面に当接する状態でスライダー３９にフリ
ー回転可能となるよう外嵌している。The multi-plate case 41 is formed in an annular shape having an L-shaped cross section and having an outer diameter substantially equal to that of the outer ring 16, and is fitted onto the slider 39 so as to be freely rotatable while the front surface abuts on the rear surface of the coupling member 40. are doing.

【００２９】この多板ケース４１とスライダー３９の間
に設けられた回転伝達機構４２は、内周がセレーション
溝５０でスライダー３９と、回転方向に一体で軸方向に
移動自在となる環状板５１と、外周が多板ケース４１と
セレーション溝５２で回転方向に一体で軸方向に移動自
在となる環状板５３を、複数づつ交互に順次重ね合わ
せ、多板ケース４１の端部に取付けた皿バネ５４によ
り、環状板５１、５３を互に圧接させて予圧を与え、更
にスライダー３９の後端部との間に縮設したスプリング
５５により、回転伝達機構４２と多板ケース４１に常時
スライダー３９の先端部に位置する弾性を付勢してい
る。The rotation transmitting mechanism 42 provided between the multi-plate case 41 and the slider 39 has a slider 39 on the inner periphery of which is a serration groove 50, and an annular plate 51 which is integrally movable in the rotational direction and axially movable. , A disc spring 54 attached to the end of the multi-plate case 41 by alternately stacking a plurality of annular plates 53, which are movable in the axial direction integrally with the multi-plate case 41 and the serration groove 52 in the rotation direction. The annular plates 51 and 53 are pressed against each other to give a preload, and a spring 55 that is contracted between the annular plates 51 and 53 and the rear end of the slider 39 causes the rotation transmission mechanism 42 and the multi-plate case 41 to always have the tip of the slider 39. It urges the elasticity located in the section.

【００３０】上記回転伝達機構４２は、各環状板５１、
５３の圧接による摩擦力でスライダー３９の回転を多板
ケース４１に伝達し、多板ケース４１に作用する負荷が
摩擦力を越えると環状板５１、５３はスリップし、スラ
イダー３９と多板ケース４１は空転することになる。The rotation transmission mechanism 42 includes annular plates 51,
Rotation of the slider 39 is transmitted to the multi-plate case 41 by the frictional force generated by the pressure contact of 53, and when the load acting on the multi-plate case 41 exceeds the frictional force, the annular plates 51 and 53 slip and the slider 39 and the multi-plate case 41 are slipped. Will spin idle.

【００３１】前記外輪１６の後端面と多板ケース４１の
前面の相対向面には、スライダー３９を内輪１８に接近
させたとき結合する歯車状の噛合い部５６、５７が形成
され、多板ケース４１の回転を外輪１６に伝達するよう
になっている。Gear-shaped meshing portions 56 and 57 are formed on the rear end surface of the outer ring 16 and the front surface of the multi-plate case 41 which face each other when the slider 39 is brought close to the inner ring 18. The rotation of the case 41 is transmitted to the outer ring 16.

【００３２】なお、スライダー３９の軸方向の移動は、
アクチュエータによるフォーク以外に、ワイヤケーブル
やデフカバー４に取付けたエアや油圧のシリンダに圧力
流体を給排することによって行なうようにしたり、これ
に代えてソレノイドを用い、スライダーの移動を電気的
な制御によって行なうようにしてもよい。The axial movement of the slider 39 is
In addition to a fork by an actuator, pressure fluid is supplied to and discharged from a wire cable or an air or hydraulic cylinder attached to the differential cover 4, or a solenoid is used instead of the pressure fluid to electrically move the slider. You may do it.

【００３３】この発明の動力伝達装置は上記のような構
成であり、次に、この装置を用いた車両の走行状態につ
いて説明する。The power transmission device of the present invention has the above-mentioned structure. Next, the running state of the vehicle using this device will be described.

【００３４】〔２駆走行モード〕２駆走行モードでは、
図３のように、スライダー３９を退動させ、噛合い部５
６、５７及び結合部材４０と噛合い部材４３を離反さ
せ、外輪１６と大径保持器２３を離開した状態におく。[Two-wheel drive mode] In the two-wheel drive mode,
As shown in FIG. 3, the slider 39 is retracted to move the engagement portion 5
6, 57 and the coupling member 40 and the meshing member 43 are separated from each other, and the outer ring 16 and the large-diameter cage 23 are kept separated.

【００３５】この状態で車輌が前進走行すると、大径保
持器２３は、スイッチバネ３７の弾性力によって内輪１
８に対し相対回転し、図９に示すようにスプラグ３２を
前進方向の係合作動位置へ移動させる。When the vehicle travels forward in this state, the large diameter cage 23 is driven by the elastic force of the switch spring 37 to cause the inner ring 1 to move.
8, the sprag 32 is moved to the engaging operation position in the forward direction as shown in FIG.

【００３６】このようにスプラグ３２が係合作動位置に
移行した状態では、車軸の回転数より上回った回転が外
輪１６に与えられた場合、スプラグ３２は係合状態を解
除し、外輪１６はフリーランニングすることができる。
このため、トランスファーより動力を切離された前輪車
軸１２は、タイヤからの駆動力によりそれぞれ回され
る。長尺側の前車輪の駆動側はディファレンシャルを介
し、短尺側の駆動軸と反対方向の回転となる。その場
合、リングギヤ５、ピニオンギヤ６、それに連結するト
ランスファーまでの駆動系は停止する。When the sprag 32 is moved to the engagement operation position as described above, if the outer ring 16 is rotated at a speed higher than the rotational speed of the axle, the sprag 32 releases the engaged state and the outer ring 16 is free. You can run.
Therefore, the front wheel axles 12, which are separated from the power by the transfer, are rotated by the driving force from the tires. The drive side of the front wheel on the long side is rotated in the opposite direction to the drive shaft on the short side via the differential. In that case, the drive system up to the ring gear 5, the pinion gear 6, and the transfer connected thereto is stopped.

【００３７】したがって、前進走行中の静粛性や燃費性
能は、従来のマニュアル式や自動式のフリーホイールハ
ブと同レベルに近く維持される。Therefore, the quietness and the fuel consumption performance during the forward traveling are maintained close to the same level as those of the conventional manual or automatic freewheel hub.

【００３８】〔４駆走行オーバランニングモード〕舗装
道路等の摩擦係数の高い路面を４駆走行する場合は、図
４のようにスライダー３９を中間位置に前進動させ、外
輪１６と大径保持器２３を切離した状態で、噛合い部５
６、５７を結合し、多板ケース４１と外輪１６を一体化
する。[4WD Overrunning Mode] When traveling on a road surface having a high friction coefficient such as a paved road by 4WD, the slider 39 is moved forward to an intermediate position as shown in FIG. 4 to move the outer ring 16 and the large diameter cage. With the 23 separated, the meshing portion 5
6, 57 are combined to integrate the multi-plate case 41 and the outer ring 16.

【００３９】これにより、駆動軸１２ａの回転は、回転
伝達機構４２と二方向クラッチａを介して外輪１６に伝
わり、前進方向において４輪駆動となり、二方向クラッ
チａによって、駆動側と従動側の回転差に応じてフリー
ランニング機能が作動する。As a result, the rotation of the drive shaft 12a is transmitted to the outer ring 16 via the rotation transmission mechanism 42 and the two-way clutch a, and four-wheel drive is performed in the forward direction, and the two-way clutch a causes the drive side and the driven side to move. The free running function operates according to the rotation difference.

【００４０】すなわち、車両が旋回して蛇角をもつと、
前輪と後輪の旋回距離の差により、前輪に連結する外輪
１６が内輪１８よりも速く回転し、外輪１６がスプラグ
３２に対してフリーランニングする。このため、前輪と
後輪は切離されて回転し、タイトコーナでのブレーキン
グ現象が生じない。That is, when the vehicle turns and has a snake angle,
Due to the difference in the turning distance between the front wheel and the rear wheel, the outer wheel 16 connected to the front wheel rotates faster than the inner wheel 18, and the outer wheel 16 runs freely with respect to the sprag 32. Therefore, the front wheel and the rear wheel are separated and rotate, and the braking phenomenon at the tight corner does not occur.

【００４１】また、エンジンブレーキ時は、回転伝達機
構４２の摩擦力のみによって動力伝達がなされる。During engine braking, power is transmitted only by the frictional force of the rotation transmitting mechanism 42.

【００４２】〔４駆走行ロックモード〕雪道等の摩擦係
数の低い路面を４駆走行する場合は、図５のように、ス
ライダー３９を最前進位置に前進動させ、噛合い部５
６、５７が結合したままで結合部材４０と噛合い部材４
３を噛み合せた状態にする。[4WD Travel Lock Mode] When traveling on a road surface having a low friction coefficient such as a snowy road by 4WD, as shown in FIG. 5, the slider 39 is moved forward to the most advanced position, and the meshing portion 5 is moved.
6, 57 and the coupling member 4 and the engaging member 4
Put 3 into the engaged state.

【００４３】これにより、外輪１６と大径保持器２３が
一体になり、大径保持器２３は外輪１６と同一方向に回
転する。このため、スプラグ３２が図９のようにフリー
ランニングの状態にある場合でも、大径保持器２３の回
転によってスプラグ３２は図１０のように傾きを変えて
外輪１６と内輪１８の円筒面２１、２２に結合し、外輪
１６のフリーランニングが停止する。したがって、外輪
１６と駆動軸１２ａが直結した状態になり、前後輪が直
結した４輪駆動状態になる。As a result, the outer ring 16 and the large-diameter retainer 23 are integrated, and the large-diameter retainer 23 rotates in the same direction as the outer ring 16. Therefore, even when the sprag 32 is in the free running state as shown in FIG. 9, the rotation of the large-diameter cage 23 causes the sprag 32 to change its inclination as shown in FIG. 10 and the cylindrical surfaces 21 of the outer ring 16 and the inner ring 18, 22 and the free running of the outer ring 16 is stopped. Therefore, the outer wheel 16 and the drive shaft 12a are directly connected to each other, and the front and rear wheels are directly connected to each other to be a four-wheel drive state.

【００４４】上記の状態では、４駆走行を２駆走行に切
換えるのに車両を後退させる必要がないため、悪路にお
いて前後進を切換えて脱出するような場合でも４駆走行
状態が維持されることになり、大きな走破力を発揮する
ことができる。In the above-mentioned state, since it is not necessary to move the vehicle backward to switch from four-wheel drive to two-wheel drive, the four-wheel drive state is maintained even in the case of switching between forward and reverse on a rough road to escape. That is, it is possible to exert a great running power.

【００４５】また、２駆走行状態で摩擦係数が低く長い
登り坂等に停止し、その後４駆走行で発進する場合で
も、瞬時に４駆状態に切換り、その切換りにタイムラグ
がないため、スムーズな発進を行なうことができると共
に、駆動時及びエンジンブレーキ時は、二方向クラッチ
ａと回転伝達機構４２により動力を伝達する。Even when the vehicle is stopped on a long uphill or the like with a low friction coefficient in the two-wheel drive state and then started in the four-wheel drive, the four-wheel drive state is instantly switched, and there is no time lag in the switching. The vehicle can be smoothly started, and power is transmitted by the two-way clutch a and the rotation transmission mechanism 42 during driving and engine braking.

【００４６】このように、この発明の動力伝達装置で
は、走行中の刻々と変わる路面の変化に幅広く対応する
ことができ、フルタイムの４輪駆動車と同様に安定した
走行を行なうことができる。As described above, the power transmission device of the present invention can widely cope with the ever-changing road surface changes during traveling, and can perform stable traveling similarly to a full-time four-wheel drive vehicle. .

【００４７】[0047]

【発明の効果】以上のように、この発明によると、二方
向クラッチの係合子の保持器を従動部材に結合部材で切
離し自在に結合できるようにしたので、任意にクラッチ
のフリーランニングを停止させることができ、駆動部材
と従動部材間でトルク伝達経路を開放状態と直結状態と
に変化させることができ、前後駆動系を切離した状態で
２駆走行できると共に、ロック機構に摩擦式の回転伝達
機構を設けたので、４駆走行時は、前車輪のオーバラン
ニングモードと、前後輪を直結するロックモードの選択
が可能になり、しかもオーバランニングモード時にも、
摩擦力の範囲でエンジンブレーキを作用させることがで
き、燃費と静粛性に優れ、路面の変化に正確に対応でき
る４輪走行を実現できる効果がある。As described above, according to the present invention, since the retainer of the engaging element of the two-way clutch can be detachably connected to the driven member by the connecting member, the free running of the clutch can be arbitrarily stopped. It is possible to change the torque transmission path between the drive member and the driven member between the open state and the direct connection state, and it is possible to drive by two-wheel drive with the front-rear drive system separated and the frictional rotation transmission to the lock mechanism. Since a mechanism is provided, it is possible to select the front wheel overrunning mode and the lock mode that directly connects the front and rear wheels when driving in 4WD, and also in the overrunning mode,
The engine brake can be applied within the range of frictional force, fuel consumption and quietness are excellent, and there is an effect that it is possible to realize four-wheel running that can accurately respond to changes in the road surface.

【００４８】また、駆動軸の分離部分に動力伝達装置を
設けることにより、動力伝達装置の設置スペースの確保
が容易になり、ホイールハブの構造を簡略化することが
できる。Further, by providing the power transmission device in the separated portion of the drive shaft, it becomes easy to secure the installation space for the power transmission device, and the structure of the wheel hub can be simplified.

【図面の簡単な説明】[Brief description of drawings]

【図１】４輪駆動車の車輪駆動系を示す平面図FIG. 1 is a plan view showing a wheel drive system of a four-wheel drive vehicle.

【図２】同上における動力伝達装置の横断平面図FIG. 2 is a transverse plan view of the power transmission device of the above.

【図３】同上における２駆走行モードの拡大断面図FIG. 3 is an enlarged cross-sectional view of a two-wheel drive mode in the same as above.

【図４】同上における４駆走行オーバランニングモード
の拡大断面図FIG. 4 is an enlarged sectional view of a four-wheel drive overrunning mode in the same as above.

【図５】同上における４駆走行ロックモードの拡大断面
図FIG. 5 is an enlarged sectional view of a four-wheel drive traveling lock mode of the same as above.

【図６】ロック手段の要部を示す分解斜視図FIG. 6 is an exploded perspective view showing a main part of a locking means.

【図７】図２の矢印VII −VII に沿う断面図FIG. 7 is a sectional view taken along the arrows VII-VII in FIG.

【図８】図２の矢印VIII−VIIIに沿う断面図FIG. 8 is a sectional view taken along arrows VIII-VIII in FIG.

【図９】スプラグの前進係合状態とフリーランニング状
態を示す断面図FIG. 9 is a sectional view showing a forward engagement state and a free running state of the sprag.

【図１０】スプラグの後退係合状態とフリーランニング
を停止した状態を示す断面図FIG. 10 is a cross-sectional view showing a state in which the sprag is in the backward engagement state and free running is stopped.

【符号の説明】[Explanation of symbols]

１ フロントディファレンシャル ２ 前車輪 ４ デフカバー １２、１３ 車軸 １２ａ、１２ｂ 駆動軸 １６ 外輪 １８ 内輪 ２１、２２ 円筒面 ２３ 大径保持器 ２４ 小径保持器 ２５ 延長腕 ２９ 圧着バネ ３０、３１ ポケット ３２ スプラグ ３７ スイッチバネ ３８ ロック手段 ３９ スライダー ４０ 結合部材 ４１ 多板ケース ４２ 回転伝達機構 ４３ 噛合い部材 ５１、５３ 環状板 ５６、５７ 噛合い部 ａ 二方向クラッチ 1 front differential 2 front wheel 4 differential cover 12, 13 axle 12a, 12b drive shaft 16 outer ring 18 inner ring 21, 22 cylindrical surface 23 large diameter retainer 24 small diameter retainer 25 extension arm 29 crimping spring 30, 31 pocket 32 sprag 37 switch spring 38 Locking means 39 Slider 40 Coupling member 41 Multi-plate case 42 Rotation transmission mechanism 43 Engaging members 51, 53 Annular plates 56, 57 Engaging part a Two-way clutch

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】 入力軸に固定した駆動部材と出力軸に固
定した従動部材の間に、複数の係合子と、各係合子を駆
動部材と従動部材に対する係合作動位置に移動させるた
めの保持器からなる二方向クラッチを組込み、前記入力
軸に外部からの遠隔操作により保持器と従動部材を切離
し自在に結合するロック手段を設け、このロック手段
が、入力軸と一体に回転し、軸方向に移動自在となるス
ライダーと、スライダーの外側に位置するケースと、ス
ライダーの回転を摩擦力でケースに伝達する回転伝達機
構とで形成され、このロック手段のケースと前記従動部
材とに、切離し自在に結合する一対の噛合い部を設けた
動力伝達装置。1. A plurality of engagement elements between a drive member fixed to an input shaft and a driven member fixed to an output shaft, and a holding member for moving each engagement element to an engagement operation position with respect to the drive member and the driven member. A two-way clutch composed of a container is incorporated, and a lock means is provided on the input shaft to detachably connect the retainer and the driven member by remote control from the outside, and the lock means rotates integrally with the input shaft, It is composed of a slider that can move freely, a case located outside the slider, and a rotation transmission mechanism that transmits the rotation of the slider to the case by frictional force, and can be separated into the case of this locking means and the driven member. A power transmission device provided with a pair of meshing portions coupled to each other. 【請求項２】 上記ロック手段を、入力軸に軸方向への
移動が自在となるよう嵌挿したスライダーと、保持器と
従動部材の一方に係合しつつ他方に設けた噛合い部に対
して接近離反する結合部材を軸方向に一体動するよう結
合し、スライダーに連結した操作用フォークで該スライ
ダーを軸方向に移動させるようにした請求項１記載の動
力伝達装置。2. A slider in which the lock means is fitted to the input shaft so as to be movable in the axial direction, and a meshing portion provided on the other side while engaging one of the retainer and the driven member. 2. The power transmission device according to claim 1, wherein coupling members that move toward and away from each other are coupled so as to integrally move in the axial direction, and the slider is moved in the axial direction by an operating fork coupled to the slider.