JP2021110377A - Drive force distribution device for vehicle - Google Patents

Abstract

To provide a drive force distribution device for a vehicle which can suppress a load in an axial direction which is received by a bearing arranged between relatively-rotatable rotating members.SOLUTION: A drive force distribution device 16 comprises: a first rotating member 4 relatively non-rotatably connected to one side gear 34 of a differential gear mechanism 3; a second rotating member 5 relatively rotatably arranged coaxially with the first rotating member 4; and an intermittent mechanism 6 which can intermit the connection between the first rotating member 4 and the second rotating member 5. A first bearing part 71 for supporting the first rotating member 4 includes an elastic member 8, and is energized in a direction in which the second rotating member 5 separates from the first rotating member 4 by a restoring force of the elastic member 8. In the second rotating member 5, a moving amount in an axial direction to the differential gear mechanism 3 side from an initial position is limited to a prescribed value or smaller at a second bearing part 72, and when the moving amount of the second rotating member 5 from the initial position is not limited, a distance in which the second rotating member 5 can move in the axial direction while compressing the elastic member 8 is longer than the prescribed value.SELECTED DRAWING: Figure 2

Description

本発明は、入力された駆動力を複数の車輪側に配分して出力する車両用駆動力配分装置に関する。 The present invention relates to a vehicle driving force distribution device that distributes and outputs the input driving force to a plurality of wheel sides.

従来、入力された駆動力を車両の左右輪に配分する駆動力配分装置には、一対の出力歯車としてのサイドギヤを有する差動歯車機構と、一対のサイドギヤのうち一方のサイドギヤに相対回転不能に連結された回転部材とドライブシャフトとの連結を断続可能な断続機構と、を備えたものがある（例えば、特許文献１参照）。 Conventionally, the driving force distribution device that distributes the input driving force to the left and right wheels of the vehicle has a differential gear mechanism having side gears as a pair of output gears and a side gear that cannot rotate relative to one of the pair of side gears. Some are provided with an intermittent mechanism capable of intermittently connecting the connected rotating member and the drive shaft (see, for example, Patent Document 1).

特許文献１に記載の駆動力配分装置は、前後輪を駆動する四輪駆動状態と前輪のみを駆動する二輪駆動状態とを切り替え可能な四輪駆動車の後輪側に搭載されており、差動歯車機構の一方のサイドギヤと一体に回転するインナシャフトと、左後輪のドライブシャフトと相対回転不能に連結される連結シャフトと、連結シャフトと一体に回転するクラッチドラム及びこのクラッチドラムとインナシャフトとの間に配置された摩擦クラッチを含むクラッチ機構と、を有している。インナシャフトには、連結シャフトの一端部を収容する収容孔が形成されており、連結シャフトの外周面と収容孔の内面との間には、インナシャフトと連結シャフトとの同心性を確保するための軸受（玉軸受）が配置されている。 The driving force distribution device described in Patent Document 1 is mounted on the rear wheel side of a four-wheel drive vehicle capable of switching between a four-wheel drive state in which the front and rear wheels are driven and a two-wheel drive state in which only the front wheels are driven. An inner shaft that rotates integrally with one side gear of the moving gear mechanism, a connecting shaft that is non-rotatably connected to the drive shaft of the left rear wheel, a clutch drum that rotates integrally with the connecting shaft, and the clutch drum and inner shaft. It has a clutch mechanism including a friction clutch arranged between and. The inner shaft is formed with an accommodating hole for accommodating one end of the connecting shaft, and in order to ensure the concentricity between the inner shaft and the connecting shaft between the outer peripheral surface of the connecting shaft and the inner surface of the accommodating hole. Bearings (ball bearings) are arranged.

差動歯車機構には、プロペラシャフトを介してエンジンの駆動力が伝達される。プロペラシャフトとエンジンとの間には、プロペラシャフトへの駆動力の伝達を遮断することが可能な噛み合いクラッチが配置されている。そして、二輪駆動状態での走行時には、噛み合いクラッチ及び摩擦クラッチを共に解放状態とすることで、プロペラシャフトを非回転にすることができ、プロペラシャフトの回転による動力損失が抑制されて燃費性能が向上する。 The driving force of the engine is transmitted to the differential gear mechanism via the propeller shaft. A meshing clutch capable of blocking the transmission of the driving force to the propeller shaft is arranged between the propeller shaft and the engine. When traveling in the two-wheel drive state, the propeller shaft can be made non-rotating by releasing both the meshing clutch and the friction clutch, and the power loss due to the rotation of the propeller shaft is suppressed to improve fuel efficiency. do.

特開２０１７−１１５９３０号公報JP-A-2017-115930

上記のように構成された四輪駆動車では、二輪駆動状態においてプロペラシャフトの回転が停止した状態で左右後輪が回転するので、連結シャフトには、右後輪のドライブシャフトの回転が差動歯車機構によって反転して伝達される。このため、インナシャフトと連結シャフトとが互いに逆方向に回転し、インナシャフトと連結シャフトとの間に配置された軸受の負担が大きくなる。特に、左後輪のドライブシャフトから走行に伴う軸方向の荷重が入力され、この荷重が連結シャフトを介して軸受に伝わると、軸受の負担がさらに大きくなり、摩耗等の損傷が発生しやすくなる。 In a four-wheel drive vehicle configured as described above, the left and right rear wheels rotate while the rotation of the propeller shaft is stopped in the two-wheel drive state, so the rotation of the drive shaft of the right rear wheel is differential to the connecting shaft. It is inverted and transmitted by the gear mechanism. Therefore, the inner shaft and the connecting shaft rotate in opposite directions, and the load on the bearing arranged between the inner shaft and the connecting shaft increases. In particular, when an axial load accompanying running is input from the drive shaft of the left rear wheel and this load is transmitted to the bearing via the connecting shaft, the load on the bearing becomes even greater and damage such as wear is likely to occur. ..

そこで、本発明は、相対回転可能な回転部材間に配置される軸受が受ける軸方向の荷重を抑制することが可能な車両用駆動力配分装置を提供することを目的とする。 Therefore, an object of the present invention is to provide a vehicle driving force distribution device capable of suppressing an axial load received by a bearing arranged between relatively rotatable rotating members.

本発明は、上記の目的を達成するため、ハウジングと、入力された駆動力を一対の出力歯車に差動を許容して配分する差動歯車機構と、前記一対の出力歯車のうち一方の出力歯車に相対回転不能に連結された第１回転部材と、前記第１回転部材と同軸上で相対回転可能に配置された第２回転部材と、前記第１回転部材と前記第２回転部材との連結を断続可能な断続機構と、を備えた車両用駆動力配分装置であって、前記第１回転部材は、第１軸受部により前記ハウジングに対して回転可能に支持され、前記第２回転部材は、第２軸受部により前記ハウジングに対して回転可能に支持され、前記第１回転部材と前記第２回転部材との径方向の相対移動が、前記第１回転部材と前記第２回転部材との間に設けられた第３軸受部によって規制され、前記第１軸受部及び前記第３軸受部の少なくとも何れかは、軸方向に圧縮された状態で配置された弾性部材を含み、前記弾性部材の復元力によって前記第２回転部材が前記第１回転部材から離間する方向に付勢されており、前記第２回転部材は、前記復元力を受けて前記差動歯車機構から軸方向に最も離間した初期位置からの前記差動歯車機構側への軸方向の移動量が、前記第２軸受部において所定値以下に制限されており、前記初期位置からの前記第２回転部材の前記差動歯車機構側への軸方向の移動量が前記第２軸受部において制限されていないとした場合に前記第２回転部材が前記弾性部材を圧縮しながら前記初期位置から前記差動歯車機構側に軸方向移動可能な距離が、前記所定値よりも長い、車両用駆動力配分装置を提供する。 In order to achieve the above object, the present invention has a housing, a differential gear mechanism that allows and distributes an input driving force to a pair of output gears while allowing differential distribution, and an output of one of the pair of output gears. A first rotating member connected to a gear so as not to rotate relative to the gear, a second rotating member arranged so as to be relatively rotatable coaxially with the first rotating member, and the first rotating member and the second rotating member. A vehicle driving force distribution device including an intermittent mechanism capable of intermittently connecting the first rotating member, the first rotating member being rotatably supported by the first bearing portion with respect to the housing, and the second rotating member. Is rotatably supported with respect to the housing by the second bearing portion, and the relative movement of the first rotating member and the second rotating member in the radial direction is caused by the first rotating member and the second rotating member. At least one of the first bearing portion and the third bearing portion, which is regulated by a third bearing portion provided between the two bearing portions, includes an elastic member arranged in a state of being compressed in the axial direction, and the elastic member. The second rotating member is urged in a direction away from the first rotating member by the restoring force of the above, and the second rotating member receives the restoring force and is most separated from the differential gear mechanism in the axial direction. The amount of movement in the axial direction from the initial position to the differential gear mechanism side is limited to a predetermined value or less in the second bearing portion, and the differential gear of the second rotating member from the initial position. Assuming that the amount of axial movement toward the mechanism side is not limited by the second bearing portion, the second rotating member compresses the elastic member and axially moves from the initial position to the differential gear mechanism side. Provided is a vehicle driving force distribution device having a movable distance longer than the predetermined value.

本発明に係る車両用駆動力配分装置によれば、相対回転可能な回転部材間に配置される軸受が受ける軸方向の荷重を抑制することが可能となる。 According to the vehicle driving force distribution device according to the present invention, it is possible to suppress the axial load received by the bearings arranged between the relatively rotatable rotating members.

本発明の実施の形態に係る駆動力配分装置が搭載された四輪駆動車の構成例を示す概略構成図である。It is a schematic block diagram which shows the structural example of the four-wheel drive vehicle which mounted the driving force distribution device which concerns on embodiment of this invention. 駆動力配分装置の一部を示す断面図である。It is sectional drawing which shows a part of the driving force distribution device. （ａ）は、第２回転部材にドライブシャフトからの軸方向荷重が加わらない初期状態における第１軸受部及び第３軸受部の周辺部を示す拡大図である。（ｂ）は、第２回転部材にドライブシャフトからの軸方向荷重が加わった負荷状態における第１軸受部及び第３軸受部の周辺部を示す拡大図である。(A) is an enlarged view showing the peripheral portions of the first bearing portion and the third bearing portion in the initial state in which the axial load from the drive shaft is not applied to the second rotating member. (B) is an enlarged view showing peripheral portions of the first bearing portion and the third bearing portion in a load state in which an axial load from a drive shaft is applied to the second rotating member. 弾性部材を示す斜視図である。It is a perspective view which shows the elastic member. （ａ）は、第２回転部材にドライブシャフトからの軸方向荷重が加わらない初期状態における第２軸受部の周辺部を示す拡大図である。（ｂ）は、第２回転部材にドライブシャフトからの軸方向荷重が加わり、第２回転部材が差動歯車機構側に移動した負荷状態における第２軸受部の周辺部を示す拡大図である。(A) is an enlarged view showing a peripheral portion of a second bearing portion in an initial state in which an axial load from a drive shaft is not applied to the second rotating member. (B) is an enlarged view showing a peripheral portion of the second bearing portion in a load state in which an axial load from the drive shaft is applied to the second rotating member and the second rotating member moves to the differential gear mechanism side. ハウジングに対する第２回転部材の移動距離が第１の実施の形態よりも大きい場合の比較例について、第２回転部材がドライブシャフトから受ける荷重によって弾性部材が完全圧縮されるまで変形した状態を示す構成図である。Regarding a comparative example in which the moving distance of the second rotating member with respect to the housing is larger than that of the first embodiment, the configuration showing the state in which the second rotating member is deformed until the elastic member is completely compressed by the load received from the drive shaft. It is a figure. 第２の実施の形態に係る駆動力配分装置の一部を示す断面図である。It is sectional drawing which shows a part of the driving force distribution apparatus which concerns on 2nd Embodiment. 第３の実施の形態に係る駆動力配分装置の一部を示す断面図である。It is sectional drawing which shows a part of the driving force distribution apparatus which concerns on 3rd Embodiment. 第４の実施の形態に係る駆動力配分装置の一部を示す断面図である。It is sectional drawing which shows a part of the driving force distribution apparatus which concerns on 4th Embodiment. 第５の実施の形態に係る四輪駆動車及び駆動力配分装置の構成例を示す概略構成図である。It is a schematic block diagram which shows the structural example of the four-wheel drive vehicle and the driving force distribution device which concerns on 5th Embodiment.

［第１の実施の形態］
本発明の第１の実施の形態について、図１乃至図５を参照して説明する。なお、以下に説明する実施の形態は、本発明を実施する上での好適な具体例として示すものであり、技術的に好ましい種々の技術的事項を具体的に例示している部分もあるが、本発明の技術的範囲は、この具体的態様に限定されるものではない。 [First Embodiment]
The first embodiment of the present invention will be described with reference to FIGS. 1 to 5. It should be noted that the embodiments described below are shown as suitable specific examples for carrying out the present invention, and there are some parts that specifically exemplify various technically preferable technical matters. , The technical scope of the present invention is not limited to this specific aspect.

（四輪駆動車の全体構成）
図１は、本発明の第１の実施の形態に係る駆動力配分装置が搭載された四輪駆動車の構成例を示す概略構成図である。この四輪駆動車１は、左右の前輪１８１，１８２がエンジン１１によって駆動され、左右の後輪１８３，１８４が電動モータ１５によって駆動される。エンジン１１の駆動力は、トランスミッション１２で変速されて前輪側の差動歯車機構１３に伝達される。差動歯車機構１３は、デフケース１３１と、デフケース１３１に固定されたピニオンシャフト１３２と、ピニオンシャフト１３２に支持された一対のピニオンギヤ１３３，１３３と、一対のピニオンギヤ１３３，１３３にギヤ軸を直交させて噛み合う一対のサイドギヤ１３４，１３４とを有している。左右の前輪１８１，１８２には、一対のサイドギヤ１３４，１３４にそれぞれ連結された左右のドライブシャフト１４１，１４２を介して駆動力が伝達される。 (Overall configuration of four-wheel drive vehicle)
FIG. 1 is a schematic configuration diagram showing a configuration example of a four-wheel drive vehicle equipped with the driving force distribution device according to the first embodiment of the present invention. In the four-wheel drive vehicle 1, the left and right front wheels 181, 182 are driven by the engine 11, and the left and right rear wheels 183 and 184 are driven by the electric motor 15. The driving force of the engine 11 is changed by the transmission 12 and transmitted to the differential gear mechanism 13 on the front wheel side. The differential gear mechanism 13 has a gear axis orthogonal to the differential case 131, the pinion shaft 132 fixed to the differential case 131, the pair of pinion gears 133 and 133 supported by the pinion shaft 132, and the pair of pinion gears 133 and 133. It has a pair of side gears 134 and 134 that mesh with each other. The driving force is transmitted to the left and right front wheels 181, 182 via the left and right drive shafts 141 and 142 connected to the pair of side gears 134 and 134, respectively.

電動モータ１５の駆動力は、駆動力配分装置１６によって左右の後輪側のドライブシャフト１７１，１７２に配分され、左側のドライブシャフト１７１から左後輪１８３に、また右側のドライブシャフト１７２から右後輪１８４に、それぞれ伝達される。駆動力配分装置１６の構成については後述する。 The driving force of the electric motor 15 is distributed to the left and right rear wheel side drive shafts 171 and 172 by the driving force distribution device 16, from the left drive shaft 171 to the left rear wheel 183, and from the right drive shaft 172 to the right rear. It is transmitted to the ring 184, respectively. The configuration of the driving force distribution device 16 will be described later.

電動モータ１５及び駆動力配分装置１６は、車載の制御装置１０によって制御される。制御装置１０は、左右の前輪１８１，１８２及び左右の後輪１８３，１８４の回転速度を検出する車輪速センサ１０１〜１０４の検出値、ステアリングホイール１９１の操舵角を検出する操舵角センサ１０５の検出値、及びアクセルペダル１９２の踏み込み量を検出するアクセルペダルセンサ１０６の検出値を取得可能であり、これらの検出値に基づいて、例えば前輪１８１，１８２のスリップ時や加速時等に電動モータ１５にモータ電流を供給して左右の後輪１８３，１８４を駆動する。 The electric motor 15 and the driving force distribution device 16 are controlled by an in-vehicle control device 10. The control device 10 detects the detection values of the wheel speed sensors 101 to 104 that detect the rotational speeds of the left and right front wheels 181, 182 and the left and right rear wheels 183 and 184, and the steering angle sensor 105 that detects the steering angle of the steering wheel 191. It is possible to acquire the value and the detected value of the accelerator pedal sensor 106 that detects the amount of depression of the accelerator pedal 192, and based on these detected values, for example, when the front wheels 181, 182 are slipping or accelerating, the electric motor 15 is used. A motor current is supplied to drive the left and right rear wheels 183 and 184.

（駆動力配分装置１６の構成）
駆動力配分装置１６は、車体に対して非回転に取り付けられたハウジング２と、電動モータ１５の出力軸１５１の回転を減速する減速機構１６１と、減速機構１６１を介して入力された電動モータ１５の駆動力を一対の出力歯車としてのサイドギヤ３４に差動を許容して配分する差動歯車機構３と、一対のサイドギヤ３４のうち一方のサイドギヤ３４に相対回転不能に連結された第１回転部材４と、第１回転部材４と同軸上で相対回転可能に配置された第２回転部材５と、第１回転部材４と第２回転部材５との連結を断続可能な断続機構６とを備えている。第２回転部材５には、右側のドライブシャフト１７２が相対回転不能に固定される。 (Structure of driving force distribution device 16)
The driving force distribution device 16 includes a housing 2 mounted non-rotatingly with respect to the vehicle body, a deceleration mechanism 161 for decelerating the rotation of the output shaft 151 of the electric motor 15, and an electric motor 15 input via the deceleration mechanism 161. A differential gear mechanism 3 that allows and distributes the driving force to the side gears 34 as a pair of output gears, and a first rotating member that is connected to one side gear 34 of the pair of side gears 34 so as not to rotate relative to each other. 4, a second rotating member 5 arranged so as to be rotatable relative to the first rotating member 4, and an intermittent mechanism 6 capable of intermittently connecting the first rotating member 4 and the second rotating member 5. ing. The drive shaft 172 on the right side is fixed to the second rotating member 5 so as not to rotate relative to each other.

差動歯車機構３は、デフケース３１と、デフケース３１に取り付けられたピニオンシャフト３２と、ピニオンシャフト３２に固定された一対のピニオンギヤ３３，３３と、一対のピニオンギヤ３３，３３にギヤ軸を直交させて噛み合う一対のサイドギヤ３４，３４とを有している。デフケース３１には、その外周にリングギヤ３０が固定されており、リングギヤ３０から電動モータ１５の駆動力が入力される。 In the differential gear mechanism 3, the gear axes are orthogonal to the differential case 31, the pinion shaft 32 attached to the differential case 31, the pair of pinion gears 33 and 33 fixed to the pinion shaft 32, and the pair of pinion gears 33 and 33. It has a pair of side gears 34, 34 that mesh with each other. A ring gear 30 is fixed to the outer periphery of the differential case 31, and the driving force of the electric motor 15 is input from the ring gear 30.

図２は、駆動力配分装置１６の一部を示す断面図である。ハウジング２は、差動歯車機構３を収容するハウジング本体２１と、断続機構６を収容するハウジング蓋体２２とを有している。ハウジング蓋体２２は、ハウジング本体２１の車幅方向一側（右側）に配置され、ボルト２３によってハウジング本体２１に締結されている。ハウジング本体２１には、ハウジング蓋体２２側に向かって軸方向に開口する凹部２１０が形成されている。 FIG. 2 is a cross-sectional view showing a part of the driving force distribution device 16. The housing 2 has a housing main body 21 for accommodating the differential gear mechanism 3 and a housing lid 22 for accommodating the intermittent mechanism 6. The housing lid 22 is arranged on one side (right side) of the housing body 21 in the vehicle width direction, and is fastened to the housing body 21 by bolts 23. The housing body 21 is formed with a recess 210 that opens axially toward the housing lid 22 side.

ハウジング蓋体２２は、大径円筒部２２１及び小径円筒部２２２と、大径円筒部２２１と小径円筒部２２２との間に設けられた円盤部２２３とを一体に有している。小径円筒部２２２には、第２回転部材５が挿通されており、第２回転部材５の外周面に弾接するシール部材２４が小径円筒部２２２内に取り付けられている。 The housing lid 22 integrally includes a large-diameter cylindrical portion 221 and a small-diameter cylindrical portion 222, and a disk portion 223 provided between the large-diameter cylindrical portion 221 and the small-diameter cylindrical portion 222. A second rotating member 5 is inserted through the small-diameter cylindrical portion 222, and a seal member 24 that comes into contact with the outer peripheral surface of the second rotating member 5 is attached inside the small-diameter cylindrical portion 222.

デフケース３１は、ハウジング本体２１に一対の円錐ころ軸受７０によって回転可能に支持されている。図２では、一方の円錐ころ軸受７０を図示している。また、図２では、デフケース３１、第１回転部材４、及び第２回転部材５の共通の回転軸線Ｏを一点鎖線で示している。以下、回転軸線Ｏに平行な方向を軸方向という。 The differential case 31 is rotatably supported by a pair of conical roller bearings 70 on the housing body 21. FIG. 2 illustrates one tapered roller bearing 70. Further, in FIG. 2, the common rotation axis O of the differential case 31, the first rotating member 4, and the second rotating member 5 is shown by a alternate long and short dash line. Hereinafter, the direction parallel to the rotation axis O is referred to as an axial direction.

断続機構６は、第２回転部材５に対して相対回転不能かつ軸方向移動可能にスプライン係合によって連結された噛み合い部材６１と、噛み合い部材６１を第１回転部材４から離間する方向に付勢するコイルばね６２と、ボビン６３１にコイル巻線６３２を巻き回してなる電磁コイル６３と、電磁コイル６３を保持する環状のヨーク６４と、ヨーク６４と軸方向に並んで配置された円盤状のアーマチャ６５と、噛み合い部材６１とアーマチャ６５との間に配置されたスラスト軸受６６とを有している。ヨーク６４は、ハウジング蓋体２２の大径円筒部２２１内に固定部材２５によって固定されている。電磁コイル６３には、制御装置１０から励磁電流が供給される。 The intermittent mechanism 6 urges the meshing member 61, which is connected to the second rotating member 5 by spline engagement so as not to rotate relative to the second rotating member 5 and is movable in the axial direction, in a direction in which the meshing member 61 is separated from the first rotating member 4. A disk-shaped armature arranged axially with the coil spring 62, the electromagnetic coil 63 formed by winding the coil winding 632 around the bobbin 631, the annular yoke 64 holding the electromagnetic coil 63, and the yoke 64. It has a 65 and a thrust bearing 66 arranged between the meshing member 61 and the armature 65. The yoke 64 is fixed by a fixing member 25 in the large-diameter cylindrical portion 221 of the housing lid 22. An exciting current is supplied to the electromagnetic coil 63 from the control device 10.

噛み合い部材６１は、第２回転部材５を挿通させる円筒部６１１と、円筒部６１１の軸方向一端部から径方向外方に張り出して設けられた環状の鍔部６１２と、鍔部６１２の軸方向一側の端面に設けられた複数の噛み合い歯６１３とを一体に有している。円筒部６１１の内側には、コイルばね６２を収容するボア６１０が形成されている。第２回転部材５における第１回転部材４側の端部には止め輪６７が取り付けられており、この止め輪６７によってコイルばね６２の一端が当接する環状の当接部材６８が係止されている。コイルばね６２の他端は、ボア６１０の奥側の端面６１０ａに当接している。止め輪６７は、第２回転部材５の軸部５２（後述）の外周面に形成された環状溝５２０に嵌着されている。 The meshing member 61 includes a cylindrical portion 611 through which the second rotating member 5 is inserted, an annular flange portion 612 provided so as to project radially outward from one end in the axial direction of the cylindrical portion 611, and an axial direction of the flange portion 612. It integrally has a plurality of meshing teeth 613 provided on one end surface. A bore 610 for accommodating the coil spring 62 is formed inside the cylindrical portion 611. A retaining ring 67 is attached to the end of the second rotating member 5 on the side of the first rotating member 4, and the annular contact member 68 to which one end of the coil spring 62 contacts is locked by the retaining ring 67. There is. The other end of the coil spring 62 is in contact with the end surface 610a on the inner side of the bore 610. The retaining ring 67 is fitted in an annular groove 520 formed on the outer peripheral surface of the shaft portion 52 (described later) of the second rotating member 5.

電磁コイル６３に通電されていないとき、アーマチャ６５は、コイルばね６２の付勢力によってハウジング蓋体２２の円盤部２２３に形成された受け面２２３ａに当接する。電磁コイル６３に通電されると、ヨーク６４に発生する磁力によってアーマチャ６５が軸方向に移動し、ヨーク６４に当接する。この際、噛み合い部材６１は、スラスト軸受６６を介してアーマチャ６５に押圧され、アーマチャ６５と共に軸方向に移動する。 When the electromagnetic coil 63 is not energized, the armature 65 comes into contact with the receiving surface 223a formed on the disk portion 223 of the housing lid 22 by the urging force of the coil spring 62. When the electromagnetic coil 63 is energized, the armature 65 moves in the axial direction due to the magnetic force generated in the yoke 64 and comes into contact with the yoke 64. At this time, the meshing member 61 is pressed by the armature 65 via the thrust bearing 66 and moves in the axial direction together with the armature 65.

第１回転部材４は、差動歯車機構３のデフケース３１内に配置されるステム部４１と、ハウジング本体２１の凹部２１０内に配置される胴部４２と、胴部４２における第２回転部材５側の端部から径方向外方に張り出して設けられた環状の鍔部４３と、鍔部４３の軸方向一側の端面に設けられた複数の噛み合い歯４４とを一体に有している。ステム部４１の端部は、差動歯車機構３の一方のサイドギヤ３４に相対回転不能に連結されている。胴部４２の中心部には、第２回転部材５側に向かって軸方向に開口する凹部４０が形成されている。断続機構６は、噛み合い部材６１が軸方向一側に移動したとき、噛み合い部材６１の噛み合い歯６１３が第１回転部材４の噛み合い歯４４と噛み合うように構成されている。 The first rotating member 4 includes a stem portion 41 arranged in the differential case 31 of the differential gear mechanism 3, a body portion 42 arranged in the recess 210 of the housing body 21, and a second rotating member 5 in the body portion 42. It integrally has an annular flange portion 43 provided so as to project outward in the radial direction from the side end portion, and a plurality of meshing teeth 44 provided on one end surface of the flange portion 43 in the axial direction. The end of the stem portion 41 is connected to one side gear 34 of the differential gear mechanism 3 so as not to rotate relative to each other. A recess 40 that opens in the axial direction toward the second rotating member 5 side is formed in the central portion of the body portion 42. The intermittent mechanism 6 is configured such that the meshing teeth 613 of the meshing member 61 mesh with the meshing teeth 44 of the first rotating member 4 when the meshing member 61 moves to one side in the axial direction.

第２回転部材５は、第１回転部材４の凹部４０内に配置された円柱状のボス部５１と、ボス部５１よりも大径で噛み合い部材６１に挿通された軸部５２と、軸部５２よりも大径の中径部５３と、中径部よりも大径でシール部材２４が弾接する大径部５４と、大径部５４よりも大径でハウジング２の外部に配置されるフランジ部５５とを一体に有している。ボス部５１は、軸部５２の軸方向端面５２ａから軸方向に突出して設けられている。フランジ部５５には、ドライブシャフト１７２が相対回転不能に取り付けられる。 The second rotating member 5 includes a columnar boss portion 51 arranged in the recess 40 of the first rotating member 4, a shaft portion 52 having a diameter larger than that of the boss portion 51 and being inserted into the meshing member 61, and a shaft portion. A medium diameter portion 53 having a diameter larger than 52, a large diameter portion 54 having a diameter larger than the medium diameter portion and having the sealing member 24 collide with each other, and a flange having a diameter larger than the large diameter portion 54 and arranged outside the housing 2. It has a part 55 integrally. The boss portion 51 is provided so as to project axially from the axial end surface 52a of the shaft portion 52. A drive shaft 172 is attached to the flange portion 55 so as not to rotate relative to each other.

四輪駆動車１の走行中に二輪駆動状態から四輪駆動状態に切り替えるとき、制御装置１０は、電動モータ１５を制御してデフケース３１を左右後輪１８３，１８４と同じ速度で回転させる。これにより、第１回転部材４と第２回転部材５及び噛み合い部材６１とが回転同期する。そして、この状態で電磁コイル６３に励磁電流を供給し、噛み合い部材６１の噛み合い歯６１３を第１回転部材４の噛み合い歯４４に噛み合わせる。これにより、第１回転部材４と第２回転部材５とが噛み合い部材６１によって相対回転不能に連結され、電動モータ１５の駆動力が左右の後輪１８３，１８４に差動を許容して配分される。 When switching from the two-wheel drive state to the four-wheel drive state while the four-wheel drive vehicle 1 is traveling, the control device 10 controls the electric motor 15 to rotate the differential case 31 at the same speed as the left and right rear wheels 183 and 184. As a result, the first rotating member 4, the second rotating member 5, and the meshing member 61 are rotationally synchronized. Then, an exciting current is supplied to the electromagnetic coil 63 in this state, and the meshing teeth 613 of the meshing member 61 are meshed with the meshing teeth 44 of the first rotating member 4. As a result, the first rotating member 4 and the second rotating member 5 are connected by the meshing member 61 so as not to rotate relative to each other, and the driving force of the electric motor 15 is distributed to the left and right rear wheels 183 and 184 with differential tolerance. NS.

一方、四輪駆動車１を四輪駆動状態から二輪駆動状態にするときは、電磁コイル６３への励磁電流の供給を停止し、コイルばね６２によって第１回転部材４と噛み合い部材６１との噛み合いが解除された後、電動モータ１５への電流供給を停止する。第１回転部材４と噛み合い部材６１との噛み合いが解除されることにより、第１回転部材４と第２回転部材５とが相対回転自在となり、デフケース３１は回転停止する。この状態で、第２回転部材５は、車両走行に伴う右後輪１８４の回転力によって右後輪１８４と同速度で同方向に回転する。一方、第１回転部材４には、左後輪１８３の回転力が差動歯車機構３によって反転して伝達され、左後輪１８３と同速度で逆方向に回転する。すなわち、第１回転部材４と第２回転部材５とが互いに逆方向に回転する。 On the other hand, when the four-wheel drive vehicle 1 is changed from the four-wheel drive state to the two-wheel drive state, the supply of the exciting current to the electromagnetic coil 63 is stopped, and the first rotating member 4 and the meshing member 61 are engaged by the coil spring 62. Is released, the current supply to the electric motor 15 is stopped. When the meshing between the first rotating member 4 and the meshing member 61 is released, the first rotating member 4 and the second rotating member 5 become relatively rotatable, and the differential case 31 stops rotating. In this state, the second rotating member 5 rotates in the same direction as the right rear wheel 184 due to the rotational force of the right rear wheel 184 accompanying the traveling of the vehicle. On the other hand, the rotational force of the left rear wheel 183 is inverted and transmitted to the first rotating member 4 by the differential gear mechanism 3, and rotates in the opposite direction at the same speed as the left rear wheel 183. That is, the first rotating member 4 and the second rotating member 5 rotate in opposite directions to each other.

（第１回転部材４及び第２回転部材５の軸受構造）
駆動力配分装置１６は、第１乃至第３軸受部７１〜７３によって第１回転部材４及び第２回転部材５を支持している。第１回転部材４は、第１軸受部７１によりハウジング２のハウジング本体２１に対して回転可能に支持され、第２回転部材５は、第２軸受部７２によりハウジング２のハウジング蓋体２２に対して回転可能に支持されている。第３軸受部７３は、第１回転部材４と第２回転部材５との間に設けられており、第１回転部材４と第２回転部材５との径方向の相対移動が第３軸受部７３によって規制されている。 (Bearing structure of the first rotating member 4 and the second rotating member 5)
The driving force distribution device 16 supports the first rotating member 4 and the second rotating member 5 by the first to third bearing portions 71 to 73. The first rotating member 4 is rotatably supported by the first bearing portion 71 with respect to the housing body 21 of the housing 2, and the second rotating member 5 is rotatably supported by the second bearing portion 72 with respect to the housing lid 22 of the housing 2. It is rotatably supported. The third bearing portion 73 is provided between the first rotating member 4 and the second rotating member 5, and the relative movement of the first rotating member 4 and the second rotating member 5 in the radial direction is the third bearing portion. It is regulated by 73.

図３（ａ）は、第２回転部材５にドライブシャフト１７２からの軸方向荷重が加わらない初期状態における第１軸受部７１及び第３軸受部７３の周辺部を示す拡大図である。図３（ｂ）は、第２回転部材５にドライブシャフト１７２からの軸方向荷重が加わった負荷状態における第１軸受部７１及び第３軸受部７３の周辺部を示す拡大図である。 FIG. 3A is an enlarged view showing the peripheral portions of the first bearing portion 71 and the third bearing portion 73 in the initial state in which the axial load from the drive shaft 172 is not applied to the second rotating member 5. FIG. 3B is an enlarged view showing peripheral portions of the first bearing portion 71 and the third bearing portion 73 in a load state in which an axial load from the drive shaft 172 is applied to the second rotating member 5.

第１軸受部７１は、外輪７１１と内輪７１２との間に複数の転動体７１３が保持された玉軸受７１０によって構成されている。複数の転動体７１３は、図略の保持器によって周方向等間隔に保持されている。玉軸受７１０は、ハウジング本体２１の凹部２１０内に配置されており、外輪７１１が凹部２１０に内嵌され、内輪７１２が第１回転部材４の胴部４２に外嵌されている。複数の転動体７１３は、球状であり、外輪７１１の内周面に形成された断面円弧状の軌道面７１１ａ及び内輪７１２の外周面に形成された断面円弧状の軌道面７１２ａを転動する。 The first bearing portion 71 is composed of ball bearings 710 in which a plurality of rolling elements 713 are held between the outer ring 711 and the inner ring 712. The plurality of rolling elements 713 are held at equal intervals in the circumferential direction by a cage (not shown). The ball bearing 710 is arranged in the recess 210 of the housing body 21, the outer ring 711 is fitted in the recess 210, and the inner ring 712 is fitted in the body 42 of the first rotating member 4. The plurality of rolling elements 713 are spherical and roll on a raceway surface 711a having an arc-shaped cross section formed on the inner peripheral surface of the outer ring 711 and a raceway surface 712a having an arc-shaped cross section formed on the outer peripheral surface of the inner ring 712.

外輪７１１は、一方の側面７１１ｂが凹部２１０に形成された当接面２１０ａに当接することにより、凹部２１０の奥側への軸方向移動が規制されている。内輪７１２は、一方の側面７１２ｂが第１回転部材４の鍔部４３に当接している。これにより、第１回転部材４の差動歯車機構３側への軸方向移動が玉軸受７１０によって規制されている。 The outer ring 711 is restricted from moving in the axial direction toward the back side of the recess 210 by having one side surface 711b abut against the contact surface 210a formed in the recess 210. One side surface 712b of the inner ring 712 is in contact with the flange portion 43 of the first rotating member 4. As a result, the axial movement of the first rotating member 4 toward the differential gear mechanism 3 is regulated by the ball bearing 710.

玉軸受７１０は、固有のアキシャル内部すきまを有しており、外輪７１１と内輪７１２とは、このアキシャル内部すきまの範囲で軸方向に相対移動可能である。ここで、アキシャル内部すきまとは、外輪７１１又は内輪７１２の何れか一方の軌道輪を固定し、固定されていない他方の軌道輪を軸方向の一側及び他側に移動させたときの他方の軌道輪の最大移動量をいう。 The ball bearing 710 has a unique axial internal clearance, and the outer ring 711 and the inner ring 712 can move relative to each other in the axial direction within the range of this axial internal clearance. Here, the axial internal clearance is the other when the raceway ring of either the outer ring 711 or the inner ring 712 is fixed and the other raceway ring which is not fixed is moved to one side and the other side in the axial direction. The maximum amount of movement of the track ring.

第３軸受部７３は、外輪７３１と内輪７３２との間に複数の転動体７３３が保持された玉軸受７３０と、玉軸受７３０の内輪７３２と軸方向に並んで配置された弾性部材８とによって構成されている。複数の転動体７３３は、球状であり、図略の保持器に保持されて外輪７３１の内周面に形成された軌道面７３１ａ及び内輪７３２の外周面に形成された軌道面７３２ａを転動する。 The third bearing portion 73 is composed of a ball bearing 730 in which a plurality of rolling elements 733 are held between the outer ring 731 and the inner ring 732, and an elastic member 8 arranged alongside the inner ring 732 of the ball bearing 730 in the axial direction. It is configured. The plurality of rolling elements 733 are spherical and are held by a cage (not shown) to roll a raceway surface 731a formed on the inner peripheral surface of the outer ring 731 and a raceway surface 732a formed on the outer peripheral surface of the inner ring 732. ..

玉軸受７３０は、第１回転部材４の凹部４０内に配置されており、外輪７３１が凹部４０に内嵌されている。外輪７３１は、一方の側面７３１ｂが凹部４０に形成された当接面４０ａに当接することにより、凹部４０の奥側への軸方向移動が規制されている。内輪７３２は、第２回転部材５のボス部５１の外周に遊嵌されており、第２回転部材５が内輪７３２に対して軸方向移動可能である。 The ball bearing 730 is arranged in the recess 40 of the first rotating member 4, and the outer ring 731 is fitted in the recess 40. The outer ring 731 is restricted from moving in the axial direction toward the back side of the recess 40 by having one side surface 731b abut against the contact surface 40a formed in the recess 40. The inner ring 732 is loosely fitted on the outer periphery of the boss portion 51 of the second rotating member 5, and the second rotating member 5 can move in the axial direction with respect to the inner ring 732.

図４は、弾性部材８を示す斜視図である。本実施の形態では、弾性部材８がウェーブワッシャであり、複数の山部８１と複数の谷部８２とを有している。弾性部材８は、内輪７３２と第２回転部材５における軸部５２の軸方向端面５２ａとの間に、軸方向に圧縮された状態で配置されており、複数の山部８１が内輪７３２の一方の側面７３２ｂに当接し、複数の谷部８２が軸部５２の軸方向端面５２ａに当接している。弾性部材８は、初期状態においても軸方向に圧縮されており、その復元力によって第２回転部材５が第１回転部材４から離間する方向に付勢され、また第１回転部材４が第２回転部材５及び噛み合い部材６１から離間する方向に付勢されている。なお、弾性部材８としては、ウェーブワッシャに限らず、例えば単一もしくは複数の皿ばねを弾性部材８として用いてもよい。 FIG. 4 is a perspective view showing the elastic member 8. In the present embodiment, the elastic member 8 is a wave washer and has a plurality of peaks 81 and a plurality of valleys 82. The elastic member 8 is arranged between the inner ring 732 and the axial end surface 52a of the shaft portion 52 of the second rotating member 5 in a state of being compressed in the axial direction, and a plurality of mountain portions 81 are arranged on one side of the inner ring 732. A plurality of valley portions 82 are in contact with the axial end surface 52a of the shaft portion 52. The elastic member 8 is compressed in the axial direction even in the initial state, and the restoring force of the elastic member 8 urges the second rotating member 5 in a direction away from the first rotating member 4, and the first rotating member 4 is second. It is urged in a direction away from the rotating member 5 and the meshing member 61. The elastic member 8 is not limited to the wave washer, and for example, a single or a plurality of disc springs may be used as the elastic member 8.

図５（ａ）は、第２回転部材５にドライブシャフト１７２からの軸方向荷重が加わらない初期状態における第２軸受部７２の周辺部を示す拡大図である。図５（ｂ）は、第２回転部材５にドライブシャフト１７２からの軸方向荷重が加わり、第２回転部材５が差動歯車機構３側に移動した負荷状態における第２軸受部７２の周辺部を示す拡大図である。図５（ａ）に示す初期状態では、第２回転部材５が、弾性部材８の復元力を受けて差動歯車機構３から軸方向に最も離間した初期位置にある。 FIG. 5A is an enlarged view showing a peripheral portion of the second bearing portion 72 in an initial state in which an axial load from the drive shaft 172 is not applied to the second rotating member 5. FIG. 5B shows a peripheral portion of the second bearing portion 72 in a load state in which an axial load from the drive shaft 172 is applied to the second rotating member 5 and the second rotating member 5 moves to the differential gear mechanism 3 side. It is an enlarged view which shows. In the initial state shown in FIG. 5A, the second rotating member 5 is in the initial position farthest in the axial direction from the differential gear mechanism 3 by receiving the restoring force of the elastic member 8.

第２軸受部７２は、外輪７２１と内輪７２２との間に複数の転動体７２３が保持された玉軸受７２０と、ハウジング蓋体２２における小径円筒部２２２の内周面に形成された環状溝２２０に嵌着された止め輪７２４と、第２回転部材５の中径部５３の外周面に形成された環状溝５３０に嵌着された止め輪７２５とによって構成されている。止め輪７２４，７２５として具体的には、例えばスナップリングやＣリングを用いることができる。 The second bearing portion 72 includes a ball bearing 720 in which a plurality of rolling elements 723 are held between the outer ring 721 and the inner ring 722, and an annular groove 220 formed on the inner peripheral surface of the small-diameter cylindrical portion 222 of the housing lid 22. The retaining ring 724 is fitted to the retaining ring 724, and the retaining ring 725 is fitted to the annular groove 530 formed on the outer peripheral surface of the middle diameter portion 53 of the second rotating member 5. Specifically, for example, a snap ring or a C ring can be used as the retaining rings 724 and 725.

複数の転動体７２３は、球状であり、図略の保持器に保持されて、外輪７２１の内周面に形成された軌道面７２１ａ及び内輪７２２の外周面に形成された軌道面７２２ａを転動する。外輪７２１は、ハウジング蓋体２２の小径円筒部２２２の内周に遊嵌されており、内輪７２２は、第２回転部材５の中径部５３の外周に遊嵌されている。 The plurality of rolling elements 723 are spherical and are held by a cage (not shown) to roll a raceway surface 721a formed on the inner peripheral surface of the outer ring 721 and a raceway surface 722a formed on the outer peripheral surface of the inner ring 722. do. The outer ring 721 is loosely fitted on the inner circumference of the small-diameter cylindrical portion 222 of the housing lid 22, and the inner ring 722 is loosely fitted on the outer circumference of the middle-diameter portion 53 of the second rotating member 5.

外輪７２１は、一方の側面７２１ｂが止め輪７２４に対向し、他方の側面７２１ｃが小径円筒部２２２に設けられた対向面２２２ａに対向している。内輪７２２は、一方の側面７２２ｂが止め輪７２５に対向し、他方の側面７２２ｃが第２回転部材５における中径部５３と大径部５４との間の段差面５３ａに対向している。 In the outer ring 721, one side surface 721b faces the retaining ring 724, and the other side surface 721c faces the facing surface 222a provided on the small-diameter cylindrical portion 222. In the inner ring 722, one side surface 722b faces the retaining ring 725, and the other side surface 722c faces the stepped surface 53a between the medium diameter portion 53 and the large diameter portion 54 of the second rotating member 5.

図５（ａ）に示す初期状態では、外輪７２１の一方の側面７２１ｂと止め輪７２４とが軸方向の隙間Ｓ１を介して対向し、外輪７２１の他方の側面７２１ｃが小径円筒部２２２の対向面２２２ａに当接する。また、内輪７２２の一方の側面７２２ｂが止め輪７２５に当接し、内輪７２２の他方の側面７２２ｃと段差面５３ａとが軸方向の隙間Ｓ２を介して対向する。 In the initial state shown in FIG. 5A, one side surface 721b of the outer ring 721 and the retaining ring 724 face each other via the axial gap S1, and the other side surface 721c of the outer ring 721 faces the small diameter cylindrical portion 222. It abuts on 222a. Further, one side surface 722b of the inner ring 722 abuts on the retaining ring 725, and the other side surface 722c of the inner ring 722 and the stepped surface 53a face each other via the axial gap S2.

一方、図５（ｂ）に示す負荷状態では、外輪７２１の一方の側面７２１ｂが止め輪７２４に当接し、外輪７２１の他方の側面７２１ｃと小径円筒部２２２の対向面２２２ａとが軸方向の隙間Ｓ３を介して対向する。また、内輪７２２の一方の側面７２２ｂと止め輪７２５とが軸方向の隙間Ｓ４を介して対向し、内輪７２２の他方の側面７２２ｃが段差面５３ａに当接する。なお、図３（ｂ）は、第２軸受部７２が図５（ｂ）に示す状態にあるときの第１軸受部７１及び第３軸受部７３の状態を示している。 On the other hand, in the load state shown in FIG. 5B, one side surface 721b of the outer ring 721 abuts on the retaining ring 724, and the other side surface 721c of the outer ring 721 and the facing surface 222a of the small diameter cylindrical portion 222 are in an axial gap. Opposing via S3. Further, one side surface 722b of the inner ring 722 and the retaining ring 725 face each other through the axial gap S4, and the other side surface 722c of the inner ring 722 abuts on the stepped surface 53a. Note that FIG. 3B shows the states of the first bearing portion 71 and the third bearing portion 73 when the second bearing portion 72 is in the state shown in FIG. 5B.

このように、第２回転部材５は、初期位置からの差動歯車機構３側への軸方向の移動量が、第２軸受部７２において所定値以下に制限されている。この所定値は、隙間Ｓ１及び隙間Ｓ２の軸方向幅と玉軸受７２０のアキシャル内部すきまとの合計値であり、隙間Ｓ３及び隙間Ｓ４の軸方向幅と玉軸受７２０のアキシャル内部すきまとの合計値でもある。なお、図５（ａ）及び（ｂ）では、説明の明確化のため、隙間Ｓ１〜Ｓ４及び玉軸受７２０のアキシャル内部すきまを誇張して図示している。 As described above, the amount of movement of the second rotating member 5 in the axial direction from the initial position toward the differential gear mechanism 3 side is limited to a predetermined value or less in the second bearing portion 72. This predetermined value is the total value of the axial width of the gap S1 and the gap S2 and the axial internal clearance of the ball bearing 720, and the total value of the axial width of the gap S3 and the gap S4 and the axial internal clearance of the ball bearing 720. But also. In addition, in FIGS.

具体的には、差動歯車機構３から離間する方向への第２回転部材５の軸方向移動が、外輪７２１の他方の側面７２１ｃが小径円筒部２２２の対向面２２２ａに当接し、かつ内輪７２２の一方の側面７２２ｂが止め輪７２５に当接することにより規制される。また、差動歯車機構３側への第２回転部材５の軸方向移動は、外輪７２１の一方の側面７２１ｂが止め輪７２４に当接し、かつ内輪７２２の他方の側面７２２ｃが段差面５３ａに当接することにより規制される。 Specifically, the axial movement of the second rotating member 5 in the direction away from the differential gear mechanism 3 causes the other side surface 721c of the outer ring 721 to abut on the facing surface 222a of the small-diameter cylindrical portion 222, and the inner ring 722. One side surface 722b is regulated by abutting the retaining ring 725. Further, in the axial movement of the second rotating member 5 toward the differential gear mechanism 3, one side surface 721b of the outer ring 721 abuts on the retaining ring 724, and the other side surface 722c of the inner ring 722 hits the stepped surface 53a. It is regulated by contact.

ところで、四輪駆動車１が二輪駆動状態で走行する際には、前述のように第１回転部材４と第２回転部材５とが互いに逆方向に回転するので、この状態でドライブシャフト１７２からの軸方向荷重が第２回転部材５に加わり、この荷重がそのまま第３軸受部７３の玉軸受７３０に負荷されると、玉軸受７３０の負担が大きくなり、摩耗等の損傷が発生しやすくなる。 By the way, when the four-wheel drive vehicle 1 travels in the two-wheel drive state, the first rotating member 4 and the second rotating member 5 rotate in opposite directions as described above, so that the drive shaft 172 is used in this state. When the axial load of the above is applied to the second rotating member 5 and this load is directly applied to the ball bearing 730 of the third bearing portion 73, the load on the ball bearing 730 becomes large and damage such as wear is likely to occur. ..

図６は、ハウジング２に対する第２回転部材５の軸方向への移動可能な距離が大きい場合の比較例について、第２回転部材５がドライブシャフト１７２から受ける荷重によって弾性部材８が完全圧縮されるまで変形した状態を図示している。この状態では、ドライブシャフト１７２からの軸方向荷重が直接的に第３軸受部７３の玉軸受７３０に負荷され、複数の転動体７３３が高い接触荷重で外輪７３１の軌道面７３１ａ及び内輪７３２の軌道面７３２ａに押し付けられながら転動し、転動体７３３や軌道面７３１ａ，７３２ａに摩耗が発生しやすくなる。また、ドライブシャフト１７２から第２回転部材５に衝撃的な荷重が加わったときには、転動体７３３や軌道面７３１ａ，７３２ａに打痕が発生しやすくなる。 FIG. 6 shows a comparative example in which the movable distance of the second rotating member 5 in the axial direction with respect to the housing 2 is large, and the elastic member 8 is completely compressed by the load received by the second rotating member 5 from the drive shaft 172. The deformed state is shown in the figure. In this state, the axial load from the drive shaft 172 is directly applied to the ball bearing 730 of the third bearing portion 73, and the plurality of rolling elements 733 have a high contact load on the raceway surface 731a of the outer ring 731 and the raceway of the inner ring 732. It rolls while being pressed against the surface 732a, and the rolling elements 733 and the raceway surfaces 731a and 732a are likely to be worn. Further, when an impact load is applied from the drive shaft 172 to the second rotating member 5, dents are likely to occur on the rolling elements 733 and the raceway surfaces 731a and 732a.

そこで、本実施の形態では、初期位置からの第２回転部材５の差動歯車機構３側への軸方向の移動量が第２軸受部７２において制限されていないとした場合に第２回転部材５が弾性部材８を圧縮しながら初期位置から差動歯車機構３側に軸方向移動可能な距離が、上記の所定値よりも長くなるように各部の寸法が設定されている。換言すれば、第２軸受部７２において、外輪７２１の一方の側面７２１ｂが止め輪７２４に当接し、かつ内輪７２２の他方の側面７２２ｃが段差面５３ａに当接したとき、弾性部材８が軸方向に完全圧縮されておらず、さらなる軸方向の弾性変形が可能な余地が残されている。 Therefore, in the present embodiment, assuming that the amount of movement of the second rotating member 5 in the axial direction from the initial position to the differential gear mechanism 3 side is not limited by the second bearing portion 72, the second rotating member The dimensions of each part are set so that the distance that 5 can move axially from the initial position to the differential gear mechanism 3 side while compressing the elastic member 8 is longer than the above-mentioned predetermined value. In other words, in the second bearing portion 72, when one side surface 721b of the outer ring 721 abuts on the retaining ring 724 and the other side surface 722c of the inner ring 722 abuts on the stepped surface 53a, the elastic member 8 abuts in the axial direction. It is not completely compressed, leaving room for further axial elastic deformation.

これにより、ドライブシャフト１７２から第２回転部材５に大きな荷重が加わったときには、この荷重が主としてハウジング蓋体２２に嵌着された止め輪７２４によって受け止められ、第３軸受部７３の玉軸受７３０に負荷される荷重は、弾性部材８の復元力の範囲に抑えられる。 As a result, when a large load is applied from the drive shaft 172 to the second rotating member 5, this load is mainly received by the retaining ring 724 fitted to the housing lid 22, and is received by the ball bearing 730 of the third bearing portion 73. The applied load is suppressed within the range of the restoring force of the elastic member 8.

（第１の実施の形態の効果）
以上説明した本発明の第１の実施の形態によれば、二輪駆動状態での走行時に外輪７３１と内輪７３２とが互いに逆転する第３軸受部７３の玉軸受７３０が受ける軸方向の荷重を抑制することができ、これにより玉軸受７３０に摩耗等の損傷が発生することが抑えられ、駆動力配分装置１６の耐久性が高められる。 (Effect of the first embodiment)
According to the first embodiment of the present invention described above, the axial load received by the ball bearing 730 of the third bearing portion 73 in which the outer ring 731 and the inner ring 732 are reversed with each other during traveling in the two-wheel drive state is suppressed. As a result, damage such as wear to the ball bearing 730 is suppressed, and the durability of the driving force distribution device 16 is enhanced.

また、弾性部材８は、初期状態においても軸方向に圧縮された状態にあるので、その復元力によって第１乃至第３軸受部７１〜７３の玉軸受７１０，７２０，７３０のアキシャル内部すきまがガタ詰めされ、第１乃至第３軸受部７１〜７３において発生する騒音や振動が抑制される。つまり、仮に弾性部材８に替えて厚みが調整されたシムを配置することにより各部の騒音や振動を抑制しようとすれば、駆動力配分装置１６の製造時において、組立の途中段階で組立体の寸法を測定し、測定結果に応じた厚さのシムを選択して組み付けを行う必要があるが、本実施の形態によれば、このような作業が不要となり、組み立てに要する工数を減らすことができる。 Further, since the elastic member 8 is in a state of being compressed in the axial direction even in the initial state, the axial internal clearances of the ball bearings 710, 720, and 730 of the first to third bearing portions 71 to 73 are loosened due to the restoring force. It is packed and noise and vibration generated in the first to third bearing portions 71 to 73 are suppressed. That is, if it is attempted to suppress noise and vibration of each part by arranging a shim whose thickness is adjusted instead of the elastic member 8, at the time of manufacturing the driving force distribution device 16, the assembly is in the middle of assembly. It is necessary to measure the dimensions, select a shim with a thickness according to the measurement result, and assemble it. However, according to this embodiment, such work becomes unnecessary and the man-hours required for assembly can be reduced. can.

またさらに、本実施の形態によれば、弾性部材８の復元力によって第１回転部材４が噛み合い部材６１から離間する方向に付勢されているので、例えば四輪駆動車１の走行に伴う振動等により、二輪駆動状態において第１回転部材４の噛み合い歯４４が噛み合い部材６１の噛み合い歯６１３に衝突してしまうことが抑止される。 Further, according to the present embodiment, since the first rotating member 4 is urged in the direction away from the meshing member 61 by the restoring force of the elastic member 8, for example, the vibration caused by the running of the four-wheel drive vehicle 1. As a result, it is possible to prevent the meshing teeth 44 of the first rotating member 4 from colliding with the meshing teeth 613 of the meshing member 61 in the two-wheel drive state.

［第２の実施の形態］
次に、本発明の第２の実施の形態について、図７を参照して説明する。図７は、本発明の第２の実施の形態に係る駆動力配分装置の一部を示す断面図である。第２の実施の形態は、弾性部材８の配置が第１の実施の形態と異なり、その他の構成は第１の実施の形態と同様である。このため、図７において、第１の実施の形態で説明したものと共通する構成要素については、図３（ａ）及び（ｂ）に付したものと同一の符号を付して重複した説明を省略する。 [Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 7 is a cross-sectional view showing a part of the driving force distribution device according to the second embodiment of the present invention. In the second embodiment, the arrangement of the elastic member 8 is different from that in the first embodiment, and the other configurations are the same as those in the first embodiment. Therefore, in FIG. 7, the components common to those described in the first embodiment are designated by the same reference numerals as those attached to FIGS. 3A and 3B, and duplicated explanations are given. Omit.

なお、後述する第３及び第４の実施の形態についても同様に、第１の実施の形態で説明したものと共通する構成要素については、第１の実施の形態のものと同一の符号を付して重複した説明を省略する。また、第２乃至第４の実施の形態において、初期状態と負荷状態で弾性部材８が軸方向に圧縮される距離は、第１の実施の形態と同様である。 Similarly, with respect to the third and fourth embodiments described later, the same components as those described in the first embodiment are designated by the same reference numerals as those of the first embodiment. The duplicate explanation is omitted. Further, in the second to fourth embodiments, the distance at which the elastic member 8 is compressed in the axial direction in the initial state and the load state is the same as in the first embodiment.

第１の実施の形態では、弾性部材８が第３軸受部７３において玉軸受７３０の内輪７３２と軸方向に並んで配置された場合について説明したが、本実施の形態では、弾性部材８が第３軸受部７３において玉軸受７３０の外輪７３１と軸方向に並んで配置されている。弾性部材８は、外輪７３１の一方の側面７３１ｂと第１回転部材４の凹部４０の当接面４０ａとの間に圧縮された状態で配置されている。内輪７３２の一方の側面７３２ｂは、第２回転部材５の軸部５２の軸方向端面５２ａに当接している。外輪７３１は、凹部４０の内周面に遊嵌されており、第１回転部材４が外輪７３１に対して軸方向に相対移動可能である。この第２の実施の形態によっても、第１の実施の形態と同様の効果が得られる。 In the first embodiment, the case where the elastic member 8 is arranged side by side with the inner ring 732 of the ball bearing 730 in the third bearing portion 73 has been described, but in the present embodiment, the elastic member 8 is the first. 3 In the bearing portion 73, the ball bearing 730 is arranged side by side with the outer ring 731 of the ball bearing 730 in the axial direction. The elastic member 8 is arranged in a compressed state between one side surface 731b of the outer ring 731 and the contact surface 40a of the recess 40 of the first rotating member 4. One side surface 732b of the inner ring 732 is in contact with the axial end surface 52a of the shaft portion 52 of the second rotating member 5. The outer ring 731 is loosely fitted on the inner peripheral surface of the recess 40, and the first rotating member 4 can move relative to the outer ring 731 in the axial direction. The same effect as that of the first embodiment can be obtained by this second embodiment.

［第３の実施の形態］
次に、本発明の第３の実施の形態について、図８を参照して説明する。図８は、本発明の第４の実施の形態に係る駆動力配分装置の一部を示す断面図である。 [Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 8 is a cross-sectional view showing a part of the driving force distribution device according to the fourth embodiment of the present invention.

本実施の形態では、弾性部材８が、第１軸受部７１の玉軸受７１０の内輪７１２と軸方向に並んで配置されている。すなわち、第１軸受部７１が玉軸受７１０と弾性部材８とを含んで構成されている。弾性部材８は、内輪７１２の一方の側面７１２ｂと第１回転部材４の鍔部４３との間に圧縮された状態で配置されている。内輪７１２は、第１回転部材４の胴部４２の外周面に遊嵌されており、第１回転部材４が内輪７１２に対して軸方向に相対移動可能である。第２回転部材５は、第１回転部材４及び第３軸受部７３の玉軸受７３０を介して弾性部材８の復元力を受け、差動歯車装置３から離間する軸方向に付勢されている。 In the present embodiment, the elastic member 8 is arranged side by side with the inner ring 712 of the ball bearing 710 of the first bearing portion 71 in the axial direction. That is, the first bearing portion 71 is configured to include the ball bearing 710 and the elastic member 8. The elastic member 8 is arranged in a compressed state between one side surface 712b of the inner ring 712 and the flange portion 43 of the first rotating member 4. The inner ring 712 is loosely fitted on the outer peripheral surface of the body portion 42 of the first rotating member 4, and the first rotating member 4 can move relative to the inner ring 712 in the axial direction. The second rotating member 5 receives the restoring force of the elastic member 8 via the ball bearing 730 of the first rotating member 4 and the third bearing portion 73, and is urged in the axial direction away from the differential gear device 3. ..

この第３の実施の形態によっても、第１の実施の形態と同様に、二輪駆動状態での走行時に第３軸受部７３の玉軸受７３０が受ける軸方向の荷重を抑制することができる。 Also in this third embodiment, similarly to the first embodiment, it is possible to suppress the axial load received by the ball bearing 730 of the third bearing portion 73 when traveling in the two-wheel drive state.

［第４の実施の形態］
次に、本発明の第４の実施の形態について、図９を参照して説明する。図９は、本発明の第４の実施の形態に係る駆動力配分装置の一部を示す断面図である。 [Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 9 is a cross-sectional view showing a part of the driving force distribution device according to the fourth embodiment of the present invention.

本実施の形態では、弾性部材８が、第１軸受部７１の玉軸受７１０の外輪７１１と軸方向に並んで配置され、外輪７１１の一方の側面７１１ｂとハウジング本体２１の凹部２１０の当接面２１０ａとの間で軸方向に圧縮されている。外輪７１１は、凹部２１０の内周面に遊嵌されており、ハウジング本体２１に対して軸方向に相対移動可能である。第２回転部材５は、第３の実施の形態と同様に、第１回転部材４及び第３軸受部７３の玉軸受７３０を介して弾性部材８の復元力を受け、差動歯車装置３から離間する軸方向に付勢されている。 In the present embodiment, the elastic member 8 is arranged side by side with the outer ring 711 of the ball bearing 710 of the first bearing portion 71 in the axial direction, and the contact surface between one side surface 711b of the outer ring 711 and the recess 210 of the housing body 21. It is compressed in the axial direction with and from 210a. The outer ring 711 is loosely fitted on the inner peripheral surface of the recess 210, and can move relative to the housing body 21 in the axial direction. Similar to the third embodiment, the second rotating member 5 receives the restoring force of the elastic member 8 via the ball bearing 730 of the first rotating member 4 and the third bearing portion 73, and receives the restoring force from the differential gear device 3. It is urged in the axial direction to separate.

この第４の実施の形態によっても、第１の実施の形態と同様に、二輪駆動状態での走行時に第３軸受部７３の玉軸受７３０が受ける軸方向の荷重を抑制することができる。 Also in this fourth embodiment, similarly to the first embodiment, it is possible to suppress the axial load received by the ball bearing 730 of the third bearing portion 73 when traveling in the two-wheel drive state.

［第５の実施の形態］
次に、本発明の第５の実施の形態について、図１０を参照して説明する。本実施の形態は、四輪駆動車１Ａ及び駆動力配分装置１６Ａの全体的な構成が第１の実施の形態とは異なる。図１０において、第１の実施の形態について説明したものと共通する部材等については、第１の実施の形態のものと同一の符号を付して重複した説明を省略する。 [Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described with reference to FIG. In the present embodiment, the overall configuration of the four-wheel drive vehicle 1A and the driving force distribution device 16A is different from that of the first embodiment. In FIG. 10, members and the like that are common to those described in the first embodiment are designated by the same reference numerals as those in the first embodiment, and duplicated description will be omitted.

この四輪駆動車１Ａは、トランスファクラッチ９１と、トランスファクラッチ９１を介してエンジン１１の駆動力が伝達されるプロペラシャフト９２を有しており、エンジン１１の駆動力が左右の前輪１８１，１８２及び左右の後輪１８３，１８４に配分される。 The four-wheel drive vehicle 1A has a transfer clutch 91 and a propeller shaft 92 in which the driving force of the engine 11 is transmitted via the transfer clutch 91, and the driving force of the engine 11 is the left and right front wheels 181 and 182. It is distributed to the left and right rear wheels 183 and 184.

トランスファクラッチ９１は、前輪側の差動歯車機構１３のデフケース１３１と一体に回転する第１噛み合い部材９１１と、第１噛み合い部材９１１と同軸上で相対回転可能に支持された第２噛み合い部材９１２と、第１噛み合い部材９１１と第２噛み合い部材９１２とを連結可能な円筒状の連結部材９１３とを有している。連結部材９１３は、図略のアクチュエータによって進退移動し、連結部材９１３が軸方向一側に移動したときは第１噛み合い部材９１１及び第２噛み合い部材９１２が連結部材９１３に噛み合って相対回転不能に連結され、連結部材９１３が軸方向他側に移動したときには、第１噛み合い部材９１１と第２噛み合い部材９１２とが相対回転自在となる。 The transfer clutch 91 includes a first meshing member 911 that rotates integrally with the differential case 131 of the differential gear mechanism 13 on the front wheel side, and a second meshing member 912 that is supported coaxially with the first meshing member 911 so as to be relatively rotatable. , Has a cylindrical connecting member 913 capable of connecting the first meshing member 911 and the second meshing member 912. The connecting member 913 moves forward and backward by an actuator (not shown), and when the connecting member 913 moves to one side in the axial direction, the first meshing member 911 and the second meshing member 912 mesh with the connecting member 913 and are connected in a relative non-rotatable manner. When the connecting member 913 moves to the other side in the axial direction, the first meshing member 911 and the second meshing member 912 become relatively rotatable.

プロペラシャフト９２には、車両前後方向の前端部にピニオンギヤ９２１が取り付けられており、このピニオンギヤ９２１が、第２噛み合い部材９１２と一体に回転するリングギヤ９２２に噛み合わされている。また、プロペラシャフト９２には、車両前後方向の後端部にピニオンギヤ９２３が取り付けられており、このピニオンギヤ９２３が、駆動力配分装置１６Ａの差動歯車装置３のデフケース３１に固定されたリングギヤ３０に噛み合わされている。差動歯車装置３の一方のサイドギヤ３４には、第１回転部材４が相対回転不能に連結されており、この第１回転部材４と同軸上で第２回転部材５が相対回転可能に配置されている。 A pinion gear 921 is attached to the front end of the propeller shaft 92 in the front-rear direction of the vehicle, and the pinion gear 921 is meshed with a ring gear 922 that rotates integrally with the second meshing member 912. A pinion gear 923 is attached to the propeller shaft 92 at the rear end in the front-rear direction of the vehicle, and the pinion gear 923 is attached to the ring gear 30 fixed to the differential case 31 of the differential gear device 3 of the driving force distribution device 16A. It is meshed. A first rotating member 4 is connected to one side gear 34 of the differential gear device 3 so as to be relatively non-rotatable, and a second rotating member 5 is arranged coaxially with the first rotating member 4 so as to be relatively rotatable. ing.

駆動力配分装置１６Ａには、第１回転部材４と第２回転部材５との連結を断続可能な断続機構として、摩擦クラッチ９３１と、この摩擦クラッチ９３１を押圧する押圧機構９３２と、摩擦クラッチ９３１を収容する有底円筒状のクラッチドラム９３３とを有するクラッチ機構９３が用いられている。クラッチドラム９３３は、第２回転部材５と相対回転不能に連結されている。 The driving force distribution device 16A includes a friction clutch 931 as an intermittent mechanism capable of intermittently connecting the first rotating member 4 and the second rotating member 5, a pressing mechanism 932 for pressing the friction clutch 931, and a friction clutch 931. A clutch mechanism 93 having a bottomed cylindrical clutch drum 933 for accommodating the clutch mechanism 93 is used. The clutch drum 933 is connected to the second rotating member 5 so as not to rotate relative to each other.

摩擦クラッチ９３１は、第１回転部材４に噛み合わされた複数のインナクラッチプレート、及びクラッチドラム９３３に噛み合わされた複数のアウタクラッチプレートを有する多板クラッチであり、これらのクラッチプレートが押圧機構９３に押圧されて摩擦接触する。押圧機構９３は、例えば油圧によって摩擦クラッチ９３１を押圧し、摩擦クラッチ９３１は、押圧機構９３の押圧力に応じた大きさの駆動力を第１回転部材４からクラッチドラム９３３に伝達する。制御装置１０は、各センサ１０１〜１０６によって検出される車両状態に応じて押圧機構９３を制御し、左右の後輪１８３，１８４に配分される駆動力を調節する。 The friction clutch 931 is a multi-plate clutch having a plurality of inner clutch plates meshed with the first rotating member 4 and a plurality of outer clutch plates meshed with the clutch drum 933, and these clutch plates are attached to the pressing mechanism 93. It is pressed and makes frictional contact. The pressing mechanism 93 presses the friction clutch 931 by, for example, hydraulic pressure, and the friction clutch 931 transmits a driving force of a magnitude corresponding to the pressing force of the pressing mechanism 93 from the first rotating member 4 to the clutch drum 933. The control device 10 controls the pressing mechanism 93 according to the vehicle state detected by the sensors 101 to 106, and adjusts the driving force distributed to the left and right rear wheels 183 and 184.

駆動力配分装置１６Ａの第１回転部材４及び第２回転部材５は、第１の実施の形態と同様の第１乃至第３軸受部７１〜７３によって支持される。この第５の実施の形態によっても、第１の実施の形態と同様の効果が得られる。なお、第２乃至第４の実施の形態に係る第１乃至第３軸受部７１〜７３を駆動力配分装置１６Ａにおける軸受支持構造として用いてもよい。 The first rotating member 4 and the second rotating member 5 of the driving force distribution device 16A are supported by the first to third bearing portions 71 to 73 similar to those in the first embodiment. The same effect as that of the first embodiment can be obtained by the fifth embodiment. The first to third bearing portions 71 to 73 according to the second to fourth embodiments may be used as the bearing support structure in the driving force distribution device 16A.

（付記）
以上、本発明を第１乃至第４の実施の形態に基づいて説明したが、これらの実施の形態は特許請求の範囲に係る発明を限定するものではない。また、各実施の形態の中で説明した特徴の組み合せの全てが発明の課題を解決するための手段に必須であるとは限らない点に留意すべきである。また、本発明は、第１乃至第５の実施の形態を適宜組み合わせて実施することも可能である。 (Additional note)
Although the present invention has been described above based on the first to fourth embodiments, these embodiments do not limit the invention according to the claims. It should also be noted that not all combinations of features described in each embodiment are essential to the means for solving the problems of the invention. Further, the present invention can be implemented by appropriately combining the first to fifth embodiments.

また、本発明は、その趣旨を逸脱しない範囲で、一部の構成を省略し、あるいは構成を追加もしくは置換して、適宜変形して実施することが可能である。例えば、上記の第１乃至第４の実施の形態では、弾性部材８を第１軸受部７１又は第３軸受部７３の一箇所に配置した場合について説明したが、これら各実施の形態を組み合わせ、第１軸受部７１及び第３軸受部７３の複数個所に弾性部材８を配置してもよい。また、本発明に係る駆動力配分装置が搭載される車両の構成は、図１及び図１０に例示したものに限らず、様々な構成の車両に本発明に係る駆動力配分装置を用いることができる。 Further, the present invention can be carried out by appropriately modifying it by omitting a part of the configurations or adding or replacing the configurations without departing from the spirit of the present invention. For example, in the first to fourth embodiments described above, the case where the elastic member 8 is arranged at one location of the first bearing portion 71 or the third bearing portion 73 has been described. Elastic members 8 may be arranged at a plurality of positions of the first bearing portion 71 and the third bearing portion 73. Further, the configuration of the vehicle on which the driving force distribution device according to the present invention is mounted is not limited to those illustrated in FIGS. 1 and 10, and the driving force distribution device according to the present invention can be used for vehicles having various configurations. can.

１６…駆動力配分装置 ２…ハウジング
３…差動歯車機構 ３４，３４…サイドギヤ（出力歯車）
４…第１回転部材 ５…第２回転部材
６…断続機構 ６１…噛み合い部材
７１…第１軸受部 ７２…第３軸受部
７３…第３軸受部 ７３０…玉軸受
７３１…外輪 ７３２…内輪
７３３…転動体 ８…弾性部材 16 ... Driving force distribution device 2 ... Housing 3 ... Differential gear mechanism 34, 34 ... Side gear (output gear)
4 ... 1st rotating member 5 ... 2nd rotating member 6 ... Intermittent mechanism 61 ... Meshing member 71 ... 1st bearing part 72 ... 3rd bearing part 73 ... 3rd bearing part 730 ... Ball bearing 731 ... Outer ring 732 ... Inner ring 733 ... Rolling body 8 ... Elastic member

Claims (3)

ハウジングと、入力された駆動力を一対の出力歯車に差動を許容して配分する差動歯車機構と、前記一対の出力歯車のうち一方の出力歯車に相対回転不能に連結された第１回転部材と、前記第１回転部材と同軸上で相対回転可能に配置された第２回転部材と、前記第１回転部材と前記第２回転部材との連結を断続可能な断続機構と、を備えた車両用駆動力配分装置であって、
前記第１回転部材は、第１軸受部により前記ハウジングに対して回転可能に支持され、
前記第２回転部材は、第２軸受部により前記ハウジングに対して回転可能に支持され、
前記第１回転部材と前記第２回転部材との径方向の相対移動が、前記第１回転部材と前記第２回転部材との間に設けられた第３軸受部によって規制され、
前記第１軸受部及び前記第３軸受部の少なくとも何れかは、軸方向に圧縮された状態で配置された弾性部材を含み、前記弾性部材の復元力によって前記第２回転部材が前記第１回転部材から離間する方向に付勢されており、
前記第２回転部材は、前記復元力を受けて前記差動歯車機構から軸方向に最も離間した初期位置からの前記差動歯車機構側への軸方向の移動量が、前記第２軸受部において所定値以下に制限されており、
前記初期位置からの前記第２回転部材の前記差動歯車機構側への軸方向の移動量が前記第２軸受部において制限されていないとした場合に前記第２回転部材が前記弾性部材を圧縮しながら前記初期位置から前記差動歯車機構側に軸方向移動可能な距離が、前記所定値よりも長い、
車両用駆動力配分装置。 A housing, a differential gear mechanism that allows and distributes the input driving force to a pair of output gears, and a first rotation that is non-rotatably connected to one of the pair of output gears. It is provided with a member, a second rotating member arranged coaxially with the first rotating member so as to be relatively rotatable, and an intermittent mechanism capable of intermittently connecting the first rotating member and the second rotating member. It is a driving force distribution device for vehicles.
The first rotating member is rotatably supported by the first bearing portion with respect to the housing.
The second rotating member is rotatably supported by the second bearing portion with respect to the housing.
The relative movement of the first rotating member and the second rotating member in the radial direction is regulated by a third bearing portion provided between the first rotating member and the second rotating member.
At least one of the first bearing portion and the third bearing portion includes an elastic member arranged in a state of being compressed in the axial direction, and the restoring force of the elastic member causes the second rotating member to make the first rotation. It is urged away from the member and
The second rotating member receives the restoring force, and the amount of movement in the axial direction from the initial position farthest in the axial direction from the differential gear mechanism to the differential gear mechanism side is the amount of movement in the second bearing portion. It is limited to the specified value or less,
The second rotating member compresses the elastic member when the amount of axial movement of the second rotating member from the initial position to the differential gear mechanism side is not limited by the second bearing portion. However, the distance that can be moved in the axial direction from the initial position to the differential gear mechanism side is longer than the predetermined value.
Vehicle driving force distribution device. 前記第３軸受部は、内輪と外輪との間に複数の転動体を配置してなる転がり軸受と、前記弾性部材とを含み、
前記弾性部材が前記内輪又は前記外輪と軸方向に並んで配置された、
請求項１に記載の車両用駆動力配分装置。 The third bearing portion includes a rolling bearing formed by arranging a plurality of rolling elements between an inner ring and an outer ring, and the elastic member.
The elastic member is arranged so as to be axially aligned with the inner ring or the outer ring.
The vehicle driving force distribution device according to claim 1. 前記断続機構は、前記第２回転部材に対して相対回転不能かつ軸方向移動可能に連結された噛み合い部材を有し、前記噛み合い部材が軸方向一側に移動したときに前記第１回転部材と噛み合うように構成されており、
前記弾性部材は、前記第１回転部材を、前記噛み合い部材から離間する方向に付勢している、
請求項２に記載の車両用駆動力配分装置。 The intermittent mechanism has a meshing member that is connected to the second rotating member so as to be relatively non-rotatable and axially movable, and when the meshing member moves axially to one side, the first rotating member and the first rotating member. It is configured to mesh and
The elastic member urges the first rotating member in a direction away from the meshing member.
The vehicle driving force distribution device according to claim 2.

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