JP6897515B2 - Driving force transmission device - Google Patents

Driving force transmission device Download PDF

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JP6897515B2
JP6897515B2 JP2017221191A JP2017221191A JP6897515B2 JP 6897515 B2 JP6897515 B2 JP 6897515B2 JP 2017221191 A JP2017221191 A JP 2017221191A JP 2017221191 A JP2017221191 A JP 2017221191A JP 6897515 B2 JP6897515 B2 JP 6897515B2
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output rotating
rotating member
bearing
driving force
pressure receiving
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JP2019090511A (en
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広幸 井上
広幸 井上
宅野　博
博 宅野
勇治 都築
勇治 都築
亮一 久保
亮一 久保
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JTEKT Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Description

本発明は、入力された駆動力を第１及び第２の出力回転部材から出力する駆動力伝達装置に関する。 The present invention relates to a driving force transmission device that outputs an input driving force from the first and second output rotating members.

従来、入力された駆動力を第１及び第２の出力回転部材から出力する駆動力伝達装置が、例えば４輪駆動車における左右一対の副駆動輪に駆動力を伝達するために用いられている（例えば、特許文献１参照）。 Conventionally, a driving force transmitting device that outputs an input driving force from the first and second output rotating members has been used to transmit the driving force to, for example, a pair of left and right auxiliary driving wheels in a four-wheel drive vehicle. (See, for example, Patent Document 1).

特許文献１に記載の駆動力伝達装置（動力伝達装置）は、左右の後輪に駆動力を出力する左右の出力軸と、駆動力が入力される入力軸に結合されたクラッチアウターと、左右の出力軸にそれぞれ結合された左右のクラッチインナーと、クラッチアウターと左右のクラッチインナーとの間にそれぞれ配置された左右の摩擦係合部材と、左右の摩擦係合部材を軸方向に押圧する左右のクラッチピストンとを備えている。 The driving force transmission device (power transmission device) described in Patent Document 1 includes left and right output shafts that output driving force to the left and right rear wheels, clutch outers coupled to input shafts to which driving force is input, and left and right. The left and right clutch inners coupled to the output shafts of the above, the left and right friction engaging members arranged between the clutch outer and the left and right clutch inners, and the left and right that press the left and right friction engaging members in the axial direction. It is equipped with a clutch piston.

クラッチアウターは、左右のクラッチインナー間に複数の軸受を介して軸方向に位置決めされたボス部と、左右の摩擦係合部材を介して伝達される左右のクラッチピストンの押圧力を支持すべくボス部から二股に分岐する左右のディスク部と、左右の摩擦係合部材の外周部を案内すべく左右のディスク部から軸方向に延びる左右のドラム部とを備えている。左右のディスク部は、それぞれの内周がボス部の外周に溶接され、左右のディスク部の間には軸方向の隙間が形成されている。そして、この隙間により、左側のクラッチピストンの押圧力が右側の摩擦係合部材に伝達されること、及び右側のクラッチピストンの押圧力が左側の摩擦係合部材に伝達されることが抑制されている。 The clutch outer is a boss that is positioned axially between the left and right clutch inners via a plurality of bearings and a boss that supports the pressing force of the left and right clutch pistons that are transmitted via the left and right friction engagement members. It is provided with left and right disc portions that bifurcate from the portions, and left and right drum portions that extend axially from the left and right disc portions to guide the outer peripheral portions of the left and right friction engaging members. The inner circumferences of the left and right discs are welded to the outer circumference of the boss, and an axial gap is formed between the left and right discs. Then, this gap suppresses the transmission of the pressing force of the clutch piston on the left side to the friction engaging member on the right side and the pressing force of the clutch piston on the right side being transmitted to the friction engaging member on the left side. There is.

国際公開第２０１１／０８９８２５号International Publication No. 2011/089825

しかし、特許文献１に記載の駆動力伝達装置では、左右のディスク部が共にボス部の外周に溶接されて一体化されているので、左右のクラッチピストンの押圧力によりクラッチアウターの全体が軸方向に動いてしまうと、やはり左側又は右側のクラッチピストンの押圧力が右側又は左側の摩擦係合部材の係合状態に影響し、押圧力の相互干渉が発生してしまう。また、クラッチアウターの軸方向移動を確実に抑止しようとすれば、各部材の寸法精度を高め、かつ複数の軸受を用いてクラッチアウターの軸受支持剛性を高めなければならず、コストが増大してしまう。 However, in the driving force transmission device described in Patent Document 1, since the left and right disc portions are both welded to the outer periphery of the boss portion and integrated, the entire clutch outer is axially driven by the pressing force of the left and right clutch pistons. If it moves to, the pressing force of the clutch piston on the left side or the right side also affects the engaged state of the friction engaging member on the right side or the left side, and mutual interference of the pressing force occurs. Further, in order to surely suppress the axial movement of the clutch outer, it is necessary to improve the dimensional accuracy of each member and to increase the bearing support rigidity of the clutch outer by using a plurality of bearings, which increases the cost. It ends up.

そこで、本発明は、コストの増大を抑制しながら、複数のクラッチが受ける押圧力が相互に干渉してしまうことを防ぐことが可能な駆動力伝達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 driving force transmission device capable of preventing the pressing forces received by a plurality of clutches from interfering with each other while suppressing an increase in cost.

本発明は、上記の目的を達成するため、入力回転部材に入力された駆動力を前記入力回転部材と同軸配置された第１及び第２の出力回転部材から出力する駆動力伝達装置であって、前記入力回転部材ならびに前記第１及び第２の出力回転部材を収容するケース部材と、前記入力回転部材と前記第１の出力回転部材との間に配置され、前記第１の出力回転部材に駆動力を伝達する第１のクラッチと、前記入力回転部材と前記第２の出力回転部材との間に配置され、前記第２の出力回転部材に駆動力を伝達する第２のクラッチと、前記第１のクラッチを軸方向に押圧する第１の押圧部材と、前記第２のクラッチを軸方向に押圧する第２の押圧部材と、前記第１の押圧部材の押圧力を前記第１のクラッチを介して受けると共に、前記第１の出力回転部材と一体に回転する第１の受圧部材と、前記第２の押圧部材の押圧力を前記第２のクラッチを介して受けると共に、前記第２の出力回転部材と一体に回転する第２の受圧部材と、前記ケース部材内に配置された複数の軸受と、を備え、前記複数の軸受は、前記入力回転部材を前記ケース部材に対する軸方向移動を規制して支持する第１の軸受と、前記第２の出力回転部材を前記入力回転部材に対して支持する第２の軸受と、前記第１の出力回転部材を前記ケース部材に対して支持する第３の軸受と、前記第１及び第２の出力回転部材の軸方向の間もしくは前記第１及び第２の受圧部材の軸方向の間に配置された第４の軸受とを含み、前記第１及び第２の軸受が前記第１の押圧部材の押圧力を前記第２の出力回転部材を介して受け、前記第３の軸受が前記第２の押圧部材の押圧力を前記第１の出力回転部材を介して受ける、駆動力伝達装置を提供する。 The present invention is a driving force transmission device that outputs the driving force input to the input rotating member from the first and second output rotating members coaxially arranged with the input rotating member in order to achieve the above object. , The case member accommodating the input rotating member and the first and second output rotating members, and the first output rotating member arranged between the input rotating member and the first output rotating member. A first clutch for transmitting a driving force, a second clutch arranged between the input rotating member and the second output rotating member, and transmitting the driving force to the second output rotating member, and the above. The first pressing member that presses the first clutch in the axial direction, the second pressing member that presses the second clutch in the axial direction, and the pressing force of the first pressing member are the first clutch. The first pressure receiving member that rotates integrally with the first output rotating member and the pressing force of the second pressing member are received via the second clutch, and the second A second pressure receiving member that rotates integrally with the output rotating member and a plurality of bearings arranged in the case member are provided, and the plurality of bearings move the input rotating member in the axial direction with respect to the case member. The first bearing that regulates and supports, the second bearing that supports the second output rotating member with respect to the input rotating member, and the first output rotating member are supported with respect to the case member. The third bearing includes a fourth bearing arranged between the axial directions of the first and second output rotating members or between the axial directions of the first and second pressure receiving members, and the first. The first and second bearings receive the pressing force of the first pressing member via the second output rotating member, and the third bearing receives the pressing force of the second pressing member at the first output. Provided is a driving force transmission device that receives via a rotating member.

本発明に係る駆動力伝達装置によれば、コストの増大を抑制しながら、複数のクラッチが受ける押圧力が相互に干渉してしまうことを防ぐことが可能となる。 According to the driving force transmission device according to the present invention, it is possible to prevent the pressing forces received by the plurality of clutches from interfering with each other while suppressing the increase in cost.

本発明の実施の形態に係る駆動力伝達装置が搭載された４輪駆動車の構成例を模式的に示す構成図である。It is a block diagram which shows typically the configuration example of the four-wheel drive vehicle equipped with the driving force transmission device which concerns on embodiment of this invention. 駆動力伝達装置を車両搭載状態における水平断面で示す断面図である。It is sectional drawing which shows the driving force transmission device in the horizontal cross section in the vehicle-mounted state. 駆動力伝達装置の要部を示す断面図である。It is sectional drawing which shows the main part of the driving force transmission device. 油圧ユニットの構成例を模式的に示す構成図である。It is a block diagram which shows the structural example of the hydraulic unit schematically. （ａ）は、第１のピストンの押圧力の受け構造を示す説明図である。（ｂ）は、第２のピストンの押圧力の受け構造を示す説明図である。(A) is an explanatory view showing a structure for receiving a pressing force of the first piston. (B) is an explanatory view showing a structure for receiving a pressing force of the second piston. 第１の変形例の第１及び第２の受圧部材の周辺部を示す断面図である。It is sectional drawing which shows the peripheral part of the 1st and 2nd pressure receiving members of the 1st modification. 第２の変形例の第１及び第２の受圧部材の周辺部を示す断面図である。It is sectional drawing which shows the peripheral part of the 1st and 2nd pressure receiving member of the 2nd modification.

［実施の形態］
本発明の実施の形態について、図面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。 [Embodiment]
Embodiments of the present invention will be described with reference to the drawings. 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.

図１は、本発明の実施の形態に係る駆動力伝達装置が搭載された４輪駆動車の構成例を模式的に示す構成図である。 FIG. 1 is a configuration diagram schematically showing a configuration example of a four-wheel drive vehicle equipped with a driving force transmission device according to an embodiment of the present invention.

４輪駆動車１は、走行用の駆動力を発生させる駆動源としてのエンジン１０２、トランスミッション１０３、左右一対の主駆動輪としての前輪１０４Ｌ，１０４Ｒ及び左右一対の副駆動輪としての後輪１０５Ｌ，１０５Ｒと、エンジン１０２の駆動力を前輪１０４Ｌ，１０４Ｒ及び後輪１０５Ｌ，１０５Ｒに伝達可能な駆動力伝達系１０１と、制御装置１０とを備えている。 The four-wheel drive vehicle 1 includes an engine 102 and a transmission 103 as a driving source for generating a driving force for traveling, front wheels 104L and 104R as a pair of left and right main driving wheels, and rear wheels 105L as a pair of left and right auxiliary driving wheels. The 105R, a driving force transmission system 101 capable of transmitting the driving force of the engine 102 to the front wheels 104L, 104R and the rear wheels 105L, 105R, and a control device 10 are provided.

この４輪駆動車１は、エンジン１０２の駆動力を前輪１０４Ｌ，１０４Ｒ及び後輪１０５Ｌ，１０５Ｒに伝達する４輪駆動状態と、エンジン１０２の駆動力を前輪１０４Ｌ，１０４Ｒのみに伝達する２輪駆動状態とを切り替え可能である。なお、本実施の形態において、各符号における「Ｌ」及び「Ｒ」は、車両の左側及び右側を示している。 The four-wheel drive vehicle 1 has a four-wheel drive state in which the driving force of the engine 102 is transmitted to the front wheels 104L and 104R and the rear wheels 105L and 105R, and a two-wheel drive state in which the driving force of the engine 102 is transmitted only to the front wheels 104L and 104R. It is possible to switch between states. In the present embodiment, "L" and "R" in each reference numeral indicate the left side and the right side of the vehicle.

駆動力伝達系１０１は、フロントディファレンシャル１１と、エンジン１０２の駆動力を車両前後方向に伝達する駆動軸としてのプロペラシャフト１０８と、エンジン１０２側からプロペラシャフト１０８側への駆動力を断続する駆動力断続装置としての噛み合いクラッチ１２と、プロペラシャフト１０８から後輪１０５Ｌ，１０５Ｒ側へ駆動力を調節可能に伝達する駆動力伝達装置２と、前輪側のドライブシャフト１０６Ｌ，１０６Ｒと、後輪側のドライブシャフト１０７Ｌ，１０７Ｒとを有する。前輪１０４Ｌ，１０４Ｒには、エンジン１０２の駆動力が常に伝達される。後輪１０５Ｌ，１０５Ｒには、噛み合いクラッチ１２、プロペラシャフト１０８、及び駆動力伝達装置２を介してエンジン１０２の駆動力が伝達される。 The driving force transmission system 101 includes a front differential 11, a propeller shaft 108 as a driving shaft that transmits the driving force of the engine 102 in the front-rear direction of the vehicle, and a driving force that intermittently transmits the driving force from the engine 102 side to the propeller shaft 108 side. The meshing clutch 12 as an intermittent device, the driving force transmitting device 2 for adjustablely transmitting the driving force from the propeller shaft 108 to the rear wheels 105L and 105R, the drive shafts 106L and 106R on the front wheel side, and the drive on the rear wheel side. It has shafts 107L and 107R. The driving force of the engine 102 is always transmitted to the front wheels 104L and 104R. The driving force of the engine 102 is transmitted to the rear wheels 105L and 105R via the meshing clutch 12, the propeller shaft 108, and the driving force transmitting device 2.

制御装置１０は、噛み合いクラッチ１２及び駆動力伝達装置２を制御する。４輪駆動車１は、制御装置１０の制御によって、４輪駆動状態では噛み合いクラッチ１２及び駆動力伝達装置２を介して後輪１０５Ｌ，１０５Ｒに駆動力が伝達され、２輪駆動状態では噛み合いクラッチ１２及び駆動力伝達装置２による駆動力の伝達が共に遮断される。これにより、２輪駆動状態ではプロペラシャフト１０８等の回転が停止するので、燃費性能の向上が図られる。 The control device 10 controls the meshing clutch 12 and the driving force transmission device 2. In the four-wheel drive vehicle 1, the driving force is transmitted to the rear wheels 105L and 105R via the meshing clutch 12 and the driving force transmission device 2 in the four-wheel drive state under the control of the control device 10, and the meshing clutch is transmitted in the two-wheel drive state. The transmission of the driving force by the 12 and the driving force transmitting device 2 is cut off. As a result, the rotation of the propeller shaft 108 and the like is stopped in the two-wheel drive state, so that the fuel efficiency performance can be improved.

フロントディファレンシャル１１は、一対の前輪側のドライブシャフト１０６Ｌ，１０６Ｒにそれぞれ連結された一対のサイドギヤ１１１、一対のサイドギヤ１１１にギヤ軸を直交させて噛合する一対のピニオンギヤ１１２、一対のピニオンギヤ１１２を支持するピニオンギヤシャフト１１３、及びこれら一対のサイドギヤ１１１と一対のピニオンギヤ１１２とピニオンギヤシャフト１１３を収容するフロントデフケース１１４を有している。フロントデフケース１１４には、トランスミッション１０３で変速されたエンジン１０２の駆動力が伝達される。 The front differential 11 supports a pair of side gears 111 connected to a pair of drive shafts 106L and 106R on the front wheel side, a pair of pinion gears 112 that mesh with the pair of side gears 111 with their gear axes orthogonal to each other, and a pair of pinion gears 112. It has a pinion gear shaft 113, and a front differential case 114 that houses the pair of side gears 111, the pair of pinion gears 112, and the pinion gear shaft 113. The driving force of the engine 102 shifted by the transmission 103 is transmitted to the front differential case 114.

噛み合いクラッチ１２は、フロントデフケース１１４と一体に回転する第１回転部材１２１と、第１回転部材１２１と軸方向に並んで配置された第２回転部材１２２と、第１回転部材１２１と第２回転部材１２２とを相対回転不能に連結することが可能なスリーブ１２３と、制御装置１０により制御されるアクチュエータ１２０とを有している。スリーブ１２３は、アクチュエータ１２０により、第１回転部材１２１及び第２回転部材１２２に噛み合う連結位置と、第２回転部材１２２にのみ噛み合う非連結位置との間を軸方向に移動する。スリーブ１２３が連結位置にあるとき、第１回転部材１２１と第２回転部材１２２とが相対回転不能に連結され、スリーブ１２３が非連結位置にあるとき、第１回転部材１２１と第２回転部材１２２とが相対回転自在となる。 The meshing clutch 12 includes a first rotating member 121 that rotates integrally with the front differential case 114, a second rotating member 122 that is arranged alongside the first rotating member 121 in the axial direction, and a first rotating member 121 and a second rotation. It has a sleeve 123 capable of connecting the member 122 so as not to rotate relative to each other, and an actuator 120 controlled by the control device 10. The sleeve 123 is axially moved by the actuator 120 between a connecting position that meshes with the first rotating member 121 and the second rotating member 122 and a non-connecting position that meshes only with the second rotating member 122. When the sleeve 123 is in the connected position, the first rotating member 121 and the second rotating member 122 are connected in a relative non-rotatable manner, and when the sleeve 123 is in the non-connected position, the first rotating member 121 and the second rotating member 122 are connected. And can rotate relative to each other.

プロペラシャフト１０８は、エンジン１０２の駆動力をフロントデフケース１１４から噛み合いクラッチ１２を介して受けて駆動力伝達装置２側に伝達する。プロペラシャフト１０８の両端部には、一対のユニバーサルジョイント１０９が取り付けられている。車両前方側のユニバーサルジョイント１０９は、噛み合いクラッチ１２の第２回転部材１２２に設けられたリングギヤ部１２２ａに噛み合うピニオンギヤシャフト１２４とプロペラシャフト１０８とを連結している。車両後方側のユニバーサルジョイント１０９は、プロペラシャフト１０８と駆動力伝達装置２のピニオンギヤシャフト２１とを連結している。 The propeller shaft 108 receives the driving force of the engine 102 from the front differential case 114 via the meshing clutch 12 and transmits the driving force to the driving force transmission device 2 side. A pair of universal joints 109 are attached to both ends of the propeller shaft 108. The universal joint 109 on the front side of the vehicle connects the pinion gear shaft 124 and the propeller shaft 108 that mesh with the ring gear portion 122a provided on the second rotating member 122 of the meshing clutch 12. The universal joint 109 on the rear side of the vehicle connects the propeller shaft 108 and the pinion gear shaft 21 of the driving force transmission device 2.

駆動力伝達装置２は、ピニオンギヤシャフト２１と、ピニオンギヤシャフト２１に噛み合って回転する中空ギヤシャフト２２と、中空ギヤシャフト２２の内側に挿通された連結シャフト２３と、中空ギヤシャフト２２から入力された駆動力を後輪側のドライブシャフト１０７Ｌ及び連結シャフト２３に伝達する機構部２４と、機構部２４に作動油を供給する油圧ユニット９とを備えている。ドライブシャフト１０７Ｌは、左後輪１０５Ｌに連結されている。ドライブシャフト１０７Ｒは、一端部が右後輪１０５Ｒに連結され、他端部が連結シャフト２３に連結されている。 The driving force transmission device 2 includes a pinion gear shaft 21, a hollow gear shaft 22 that meshes with the pinion gear shaft 21 and rotates, a connecting shaft 23 inserted inside the hollow gear shaft 22, and a drive input from the hollow gear shaft 22. It includes a mechanism unit 24 that transmits force to the drive shaft 107L and the connecting shaft 23 on the rear wheel side, and a hydraulic unit 9 that supplies hydraulic oil to the mechanism unit 24. The drive shaft 107L is connected to the left rear wheel 105L. One end of the drive shaft 107R is connected to the right rear wheel 105R, and the other end is connected to the connecting shaft 23.

制御装置１０は、４輪駆動状態において、例えば前輪１０４Ｌ，１０４Ｒの平均回転速度と後輪１０５Ｌ，１０５Ｒの平均回転速度との差である差動回転速度が高いほど、また運転者によるアクセルペダルの踏み込み操作量が大きいほど、後輪１０５Ｌ，１０５Ｒに大きな駆動力が伝達されるように駆動力伝達装置２を制御する。また、制御装置１０は、例えば旋回時において後輪１０５Ｌ，１０５Ｒのうち旋回外側にあたる車輪に伝達される駆動力を旋回内側にあたる車輪に伝達される駆動力よりも大きくして旋回を円滑にしたり、オーバーステアやアンダーステアが発生したときに後輪１０５Ｌ，１０５Ｒのそれぞれに伝達される駆動力を調節して走行状態を安定化させるスタビリティ制御を実行する。 In the four-wheel drive state, the control device 10 has a higher differential rotation speed, which is the difference between the average rotation speed of the front wheels 104L and 104R and the average rotation speed of the rear wheels 105L and 105R. The driving force transmission device 2 is controlled so that a larger driving force is transmitted to the rear wheels 105L and 105R as the stepping operation amount is larger. Further, for example, when turning, the control device 10 makes the driving force transmitted to the wheels on the outer side of the turning larger than the driving force transmitted to the wheels on the inner side of the turning to facilitate the turning. Stability control is performed to stabilize the running state by adjusting the driving force transmitted to each of the rear wheels 105L and 105R when oversteer or understeer occurs.

図２は、駆動力伝達装置２を車両搭載状態における水平断面で示す断面図である。図３は、駆動力伝達装置２の要部を示す断面図である。 FIG. 2 is a cross-sectional view showing the driving force transmission device 2 in a horizontal cross section in a vehicle-mounted state. FIG. 3 is a cross-sectional view showing a main part of the driving force transmission device 2.

駆動力伝達装置２は、ピニオンギヤシャフト２１、中空ギヤシャフト２２、連結シャフト２３、機構部２４、及び油圧ユニット９の一部を収容するケース部材３を有している。機構部２４は、中空ギヤシャフト２２から駆動力が入力される入力回転部材４と、入力回転部材４に入力された駆動力を出力する第１及び第２の出力回転部材５，６と、入力回転部材４と第１及び第２の出力回転部材５，６との間に配置された第１及び第２のクラッチ７１，７２ならびに第１及び第２の受圧部材７３，７４と、第１及び第２のクラッチ７１，７２を押圧する第１及び第２のピストン７５，７６と、ケース部材３内に配置された複数の軸受８０〜８９とを備えている。 The driving force transmission device 2 includes a pinion gear shaft 21, a hollow gear shaft 22, a connecting shaft 23, a mechanism portion 24, and a case member 3 that houses a part of the hydraulic unit 9. The mechanism unit 24 includes an input rotating member 4 to which a driving force is input from the hollow gear shaft 22, and first and second output rotating members 5 and 6 to output the driving force input to the input rotating member 4. The first and second clutches 71 and 72 and the first and second pressure receiving members 73 and 74 arranged between the rotating member 4 and the first and second output rotating members 5 and 6, and the first and second clutches 71 and 72. It includes first and second pistons 75 and 76 for pressing the second clutches 71 and 72, and a plurality of bearings 80 to 89 arranged in the case member 3.

ケース部材３は、主としてピニオンギヤシャフト２１、中空ギヤシャフト２２、及び連結シャフト２３を収容する第１ケーシング３１と、主として機構部２４を収容する第２ケーシング３２と、第１ケーシング３１との間に第２ケーシング３２を挟む第３ケーシング３３とを有している。第１ケーシング３１と第２ケーシング３２、及び第２ケーシング３２と第３ケーシング３３は、図略のボルトによって締結されている。図２では、第１ケーシング３１と第２ケーシング３２とを位置決めする位置決めピン３４１，３４２を図示している。 The case member 3 is provided between the first casing 31 that mainly houses the pinion gear shaft 21, the hollow gear shaft 22, and the connecting shaft 23, the second casing 32 that mainly houses the mechanical portion 24, and the first casing 31. It has a third casing 33 that sandwiches the two casings 32. The first casing 31 and the second casing 32, and the second casing 32 and the third casing 33 are fastened by bolts (not shown). FIG. 2 illustrates the positioning pins 341 and 342 that position the first casing 31 and the second casing 32.

ピニオンギヤシャフト２１は、一対の軸受８０，８１に支持された軸部２１１と、軸部２１１の一端部に設けられたギヤ部２１２と、軸部２１１の他端部に設けられた連結部２１３とを有している。連結部２１３には、車両後方側のユニバーサルジョイント１０９が連結される。軸受８０，８１は、円錐ころ軸受である。ピニオンギヤシャフト２１は、車両前後方向に沿う回転軸線Ｏ１を中心として回転する。 The pinion gear shaft 21 includes a shaft portion 211 supported by a pair of bearings 80 and 81, a gear portion 212 provided at one end of the shaft portion 211, and a connecting portion 213 provided at the other end of the shaft portion 211. have. A universal joint 109 on the rear side of the vehicle is connected to the connecting portion 213. Bearings 80 and 81 are conical roller bearings. Pinion gear shaft 21 rotates about the rotation axis O 1 along the longitudinal direction of the vehicle.

中空ギヤシャフト２２は、ピニオンギヤシャフト２１のギヤ部２１２に噛み合うリングギヤ２２１と、リングギヤ２２１と一体に回転する円筒状の中空軸２２２とを有している。本実施の形態では、リングギヤ２２１と中空軸２２２とが溶接により結合されているが、これらを一体に成形してもよく、例えばボルト等の固定具によって相互に固定してもよい。中空ギヤシャフト２２及び連結シャフト２３は、車幅方向に沿う回転軸線Ｏ２を中心として回転する。以下、回転軸線Ｏ２に平行な方向を軸方向という。 The hollow gear shaft 22 has a ring gear 221 that meshes with the gear portion 212 of the pinion gear shaft 21, and a cylindrical hollow shaft 222 that rotates integrally with the ring gear 221. In the present embodiment, the ring gear 221 and the hollow shaft 222 are connected by welding, but these may be integrally formed or fixed to each other by a fixture such as a bolt. The hollow gear shaft 22 and the connecting shaft 23 rotate about the rotation axis O 2 along the vehicle width direction. Hereinafter, the direction parallel to the rotation axis O 2 is referred to as an axial direction.

中空軸２２２は、その両端部が一対の軸受８２，８３によって支持されている。軸受８２，８３は、円錐ころ軸受であり、軸方向の位置がシム３５１，３５２によって調整されると共に予圧が付与されている。そして、このシム調整によってリングギヤ２２１とピニオンギヤシャフト２１のギヤ部２１２との噛み合いが適正化されている。中空軸２２２は、第２ケーシング３２内に一端部が収容され、この一端部における外周に機構部２４の入力回転部材４との連結のための外周スプライン嵌合部２２２ａ（図３参照）が形成されている。 Both ends of the hollow shaft 222 are supported by a pair of bearings 82 and 83. The bearings 82 and 83 are conical roller bearings, and their axial positions are adjusted by shims 351 and 352 and preload is applied. Then, by this shim adjustment, the meshing between the ring gear 221 and the gear portion 212 of the pinion gear shaft 21 is optimized. One end of the hollow shaft 222 is housed in the second casing 32, and an outer peripheral spline fitting portion 222a (see FIG. 3) for connecting the mechanism portion 24 to the input rotating member 4 is formed on the outer periphery of the one end portion. Has been done.

リングギヤ２２１及びピニオンギヤシャフト２１のギヤ部２１２は、ハイポイトギヤからなり、第１ケーシング３１の第１収容空間３１０に封入された図略のギヤオイルによって噛み合いが潤滑される。第１ケーシング３１におけるピニオンギヤシャフト２１の導出口３１ａ及び連結シャフト２３の導出口３１ｂには、シール部材３６１，３６２が配置されている。 The ring gear 221 and the gear portion 212 of the pinion gear shaft 21 are composed of hypoit gears, and the meshing is lubricated by the gear oil (not shown) sealed in the first accommodation space 310 of the first casing 31. Seal members 361 and 362 are arranged at the outlet 31a of the pinion gear shaft 21 and the outlet 31b of the connecting shaft 23 in the first casing 31.

連結シャフト２３は、その両端部が中空軸２２２から軸方向に突出している。連結シャフト２３における導出口３１ｂ側の端部の内側には、ドライブシャフト１０７Ｒの図略の等速ジョイントのステム部が相対回転不能に嵌合される内周スプライン嵌合部２３ａが形成されている。また、連結シャフト２３における導出口３１ｂとは反対側の端部の外周には、機構部２４の第２の出力回転部材６との連結のための外周スプライン嵌合部２３ｂ（図３参照）が形成されている。連結シャフト２３は、外周スプライン嵌合部２３ｂが形成された側の端部近傍が、中空軸２２２の内面に嵌着された円筒状のスリップリング２５によって支持されている。 Both ends of the connecting shaft 23 project axially from the hollow shaft 222. An inner peripheral spline fitting portion 23a in which the stem portion of the constant velocity joint (not shown) of the drive shaft 107R is fitted so as not to rotate relative to each other is formed inside the end portion of the connecting shaft 23 on the side of the outlet 31b. .. Further, on the outer periphery of the end portion of the connecting shaft 23 opposite to the outlet 31b, an outer peripheral spline fitting portion 23b (see FIG. 3) for connecting the mechanism portion 24 to the second output rotating member 6 is provided. It is formed. The connecting shaft 23 is supported by a cylindrical slip ring 25 fitted to the inner surface of the hollow shaft 222 near the end on the side where the outer peripheral spline fitting portion 23b is formed.

入力回転部材４は、有底円筒状のクラッチドラム４１と、クラッチドラム４１の内側に配置された筒体４２とを有し、クラッチドラム４１と筒体４２とが溶接により一体に接合されている。クラッチドラム４１は、円筒状の円筒部４１１と、円筒部４１１の軸方向一端部から径方向内方に延在する底部４１２とを一体に有している。円筒部４１１の内周面には、軸方向に延びる複数のスプライン突起４１１ａが設けられている。 The input rotating member 4 has a bottomed cylindrical clutch drum 41 and a tubular body 42 arranged inside the clutch drum 41, and the clutch drum 41 and the tubular body 42 are integrally joined by welding. .. The clutch drum 41 integrally has a cylindrical cylindrical portion 411 and a bottom portion 412 extending inward in the radial direction from one end in the axial direction of the cylindrical portion 411. A plurality of spline protrusions 411a extending in the axial direction are provided on the inner peripheral surface of the cylindrical portion 411.

筒体４２は、中空軸２２２の外周スプライン嵌合部２２２ａが嵌合する内周スプライン嵌合部４２１ａが内周に形成された連結筒部４２１と、後述する軸受８５の外輪８５１を支持する支持筒部４２２と、連結筒部４２１と支持筒部４２２との間に設けられた環状の基部４２３とを一体に有している。筒体４２は、内周スプライン嵌合部４２１ａと中空軸２２２の外周スプライン嵌合部２２２ａとの嵌合により、中空軸２２２に対して軸方向に相対移動可能かつ相対回転不能に連結されている。連結筒部４２１の外周面には、第２ケーシング３２において中空軸２２２及び連結シャフト２３を挿通させる挿通孔の内面に取り付けられたシール部材３６３が弾接している。また、基部４２３には、その内周面に開口する環状溝４２３ａが形成され、この環状溝４２３ａに弾性体からなるＸリング３６４が収容されている。 The tubular body 42 supports the connecting tubular portion 421 in which the inner peripheral spline fitting portion 421a into which the outer peripheral spline fitting portion 222a of the hollow shaft 222 is fitted is formed on the inner circumference, and the outer ring 851 of the bearing 85 described later. It integrally has a tubular portion 422 and an annular base portion 423 provided between the connecting tubular portion 421 and the support tubular portion 422. The tubular body 42 is connected to the hollow shaft 222 so as to be relatively movable and non-rotatable in the axial direction by fitting the inner spline fitting portion 421a and the outer peripheral spline fitting portion 222a of the hollow shaft 222. .. On the outer peripheral surface of the connecting cylinder portion 421, a seal member 363 attached to the inner surface of the insertion hole through which the hollow shaft 222 and the connecting shaft 23 are inserted in the second casing 32 is elastically contacted. Further, the base portion 423 is formed with an annular groove 423a that opens on the inner peripheral surface thereof, and the annular groove 423a accommodates an X ring 364 made of an elastic body.

クラッチドラム４１と筒体４２とは、底部４１２の内周面と基部４２３の外周面とが溶接されて一体化されている。また、筒体４２の基部４２３には、その外周端部における連結筒部４２１側の角部に切り欠き４２３ｂが設けられており、この切り欠き４２３ｂに軸受８４の内径側の一部が収容されている。 The clutch drum 41 and the tubular body 42 are integrated by welding the inner peripheral surface of the bottom portion 412 and the outer peripheral surface of the base portion 423. Further, the base portion 423 of the tubular body 42 is provided with a notch 423b at a corner portion on the connecting tubular portion 421 side at the outer peripheral end portion thereof, and a part of the inner diameter side of the bearing 84 is accommodated in the notch 423b. ing.

軸受８４は、スラスト針状ころ軸受であり、インナレース８４１及びアウタレース８４２と、インナレース８４１とアウタレース８４２との間に配置された複数のころ８４３とを有している。インナレース８４１は、クラッチドラム４１の底部４１２における軸方向端面、及び筒体４２の基部４２３の切り欠き４２３ｂにおける軸方向端面に対向している。アウタレース８４２は、第２ケーシング３２の受面３２ａに対向している。この受面３２ａは、第２ケーシング３２における第３ケーシング３３側の軸方向端面の一部である。軸受８４は、入力回転部材４を、ケース部材３に対する第１収容空間３１０側への軸方向移動を規制して支持している。 The bearing 84 is a thrust needle roller bearing, and has an inner race 841 and an outer race 842, and a plurality of rollers 843 arranged between the inner race 841 and the outer race 842. The inner race 841 faces the axial end face of the bottom 412 of the clutch drum 41 and the axial end face of the notch 423b of the base 423 of the tubular body 42. The outer race 842 faces the receiving surface 32a of the second casing 32. The receiving surface 32a is a part of the axial end surface of the second casing 32 on the third casing 33 side. The bearing 84 supports the input rotating member 4 by restricting the axial movement of the input rotating member 4 toward the first accommodation space 310 with respect to the case member 3.

第１及び第２の出力回転部材５，６は、入力回転部材４と同軸配置されており、回転軸線Ｏ２を中心として回転する。第１の出力回転部材５と第２の出力回転部材６とは、軸方向に並んで配置され、第１の出力回転部材５が第３ケーシング３３側に、第２の出力回転部材６が第１ケーシング３１側に、それぞれ配置されている。 First and second output rotary members 5 and 6, the input rotary member 4 and are coaxially arranged to rotate about a rotation axis O 2. The first output rotating member 5 and the second output rotating member 6 are arranged side by side in the axial direction, the first output rotating member 5 is on the third casing 33 side, and the second output rotating member 6 is second. It is arranged on each casing 31 side.

第１の出力回転部材５は、回転軸線Ｏ２を中心軸とする円盤部５１と、円盤部５１の外径側の端部から軸方向一側に突出してクラッチドラム４１の円筒部４１１の内側に配置された大径円筒部５２と、円盤部５１の径方向略中央部から軸方向一側に突出して大径円筒部５２の内側に設けられた小径円筒部５３と、小径円筒部５３よりも径方向内側において円盤部５１から軸方向他側に突出した軸状のボス部５４とを一体に有している。 The first output rotating member 5 projects from the disk portion 51 centered on the rotation axis O 2 and the end portion on the outer diameter side of the disk portion 51 to one side in the axial direction, and is inside the cylindrical portion 411 of the clutch drum 41. From the large-diameter cylindrical portion 52 arranged in, the small-diameter cylindrical portion 53 provided inside the large-diameter cylindrical portion 52 protruding axially from the substantially central portion in the radial direction of the disk portion 51, and the small-diameter cylindrical portion 53. Also has a shaft-shaped boss portion 54 that protrudes from the disk portion 51 to the other side in the axial direction on the inner side in the radial direction.

大径円筒部５２の外周面には、軸方向に延びる複数のスプライン突起５２ａが設けられている。小径円筒部５３には、ドライブシャフト１０７Ｌの図略の等速ジョイントのステム部が相対回転不能に嵌合される内周スプライン嵌合部５３ａが形成されている。ボス部５４は、連結シャフト２３と軸方向に並んで配置されている。第３ケーシング３３には、小径円筒部５３を導出する導出口３３ａが形成されており、この導出口３３ａに配置されたシール部材３６５が小径円筒部５３の外周面に弾接している。 A plurality of spline protrusions 52a extending in the axial direction are provided on the outer peripheral surface of the large-diameter cylindrical portion 52. The small-diameter cylindrical portion 53 is formed with an inner peripheral spline fitting portion 53a in which the stem portion of the constant velocity joint (not shown) of the drive shaft 107L is fitted so as not to rotate relative to each other. The boss portion 54 is arranged alongside the connecting shaft 23 in the axial direction. A lead-out port 33a for leading out the small-diameter cylindrical portion 53 is formed in the third casing 33, and the seal member 365 arranged at the lead-out port 33a is in elastic contact with the outer peripheral surface of the small-diameter cylindrical portion 53.

第２の出力回転部材６は、第１の出力回転部材５のボス部５４の径方向外側に配置された円盤部６１と、円盤部６１の外径側の端部から軸方向に突出してクラッチドラム４１の円筒部４１１の内側に配置された大径円筒部６２と、円盤部６１の内径側の端部から軸方向に突出して大径円筒部６２の内側に設けられた小径円筒部６３とを一体に有している。円盤部６１は、第１の出力回転部材５の円盤部５１と軸方向に対向し、これら両円筒部５１，６１の間には軸方向の隙間Ｓ１が形成されている。 The second output rotating member 6 is a clutch that projects axially from a disk portion 61 arranged radially outside the boss portion 54 of the first output rotating member 5 and an end portion on the outer diameter side of the disk portion 61. A large-diameter cylindrical portion 62 arranged inside the cylindrical portion 411 of the drum 41, and a small-diameter cylindrical portion 63 provided inside the large-diameter cylindrical portion 62 protruding in the axial direction from the end on the inner diameter side of the disk portion 61. Is integrally possessed. Disk portion 61 is opposed to the first disc portion 51 and the axial direction of the output rotary member 5, a gap S 1 in the axial direction is formed between these two cylindrical portions 51 and 61.

第２の出力回転部材６の大径円筒部６２は、第１の出力回転部材５の大径円筒部５２と同径であり、筒体４２の支持筒部４２２の外側に配置されている。また、大径円筒部６２の円盤部６１からの突出方向は、第１の出力回転部材５における大径円筒部５２の円盤部５１からの突出方向とは逆方向である。大径円筒部６２の外周面には、軸方向に延びる複数のスプライン突起６２ａが設けられている。小径円筒部６３は、筒体４２の内側に配置されており、その外周面にＸリング３６４が弾接している。小径円筒部６３には、連結シャフト２３の外周スプライン嵌合部２３ｂが相対回転不能に嵌合する内周スプライン嵌合部６３ａが形成されている。 The large-diameter cylindrical portion 62 of the second output rotating member 6 has the same diameter as the large-diameter cylindrical portion 52 of the first output rotating member 5, and is arranged outside the support cylindrical portion 422 of the tubular body 42. Further, the protruding direction of the large-diameter cylindrical portion 62 from the disk portion 61 is opposite to the protruding direction of the large-diameter cylindrical portion 52 of the first output rotating member 5 from the disk portion 51. A plurality of spline protrusions 62a extending in the axial direction are provided on the outer peripheral surface of the large-diameter cylindrical portion 62. The small-diameter cylindrical portion 63 is arranged inside the tubular body 42, and the X ring 364 is in bullet contact with the outer peripheral surface thereof. The small-diameter cylindrical portion 63 is formed with an inner peripheral spline fitting portion 63a in which the outer peripheral spline fitting portion 23b of the connecting shaft 23 is fitted so as not to rotate relative to each other.

第１のクラッチ７１は、軸方向に沿って交互に配置された複数のアウタクラッチプレート７１１及び複数のインナクラッチプレート７１２からなる多板の摩擦クラッチである。アウタクラッチプレート７１１は、その外径側の端部に形成された複数の係合突起７１１ａがクラッチドラム４１のスプライン突起４１１ａに係合しており、クラッチドラム４１に対して軸方向移動可能かつ相対回転不能である。インナクラッチプレート７１２は、その内径側の端部に形成された複数の係合突起７１２ａが第１の出力回転部材５の大径円筒部５２のスプライン突起５２ａに係合しており、第１の出力回転部材５に対して軸方向移動可能かつ相対回転不能である。 The first clutch 71 is a multi-plate friction clutch composed of a plurality of outer clutch plates 711 and a plurality of inner clutch plates 712 alternately arranged along the axial direction. In the outer clutch plate 711, a plurality of engaging protrusions 711a formed at the end on the outer diameter side are engaged with the spline protrusions 411a of the clutch drum 41, and are axially movable and relative to the clutch drum 41. It cannot rotate. In the inner clutch plate 712, a plurality of engaging protrusions 712a formed at the end on the inner diameter side thereof are engaged with the spline protrusions 52a of the large-diameter cylindrical portion 52 of the first output rotating member 5, and the first It is movable in the axial direction and cannot rotate relative to the output rotating member 5.

第２のクラッチ７２は、第１のクラッチ７１と同様、軸方向に沿って交互に配置された複数のアウタクラッチプレート７２１及び複数のインナクラッチプレート７２２からなる多板の摩擦クラッチである。アウタクラッチプレート７２１は、その外径側の端部に形成された複数の係合突起７２１ａがクラッチドラム４１のスプライン突起４１１ａに係合しており、クラッチドラム４１に対して軸方向移動可能かつ相対回転不能である。インナクラッチプレート７２２は、その内径側の端部に形成された複数の係合突起７２２ａが第２の出力回転部材６の大径円筒部６２のスプライン突起６２ａに係合しており、第２の出力回転部材６に対して軸方向移動可能かつ相対回転不能である。 Like the first clutch 71, the second clutch 72 is a multi-plate friction clutch composed of a plurality of outer clutch plates 721 and a plurality of inner clutch plates 722 arranged alternately along the axial direction. In the outer clutch plate 721, a plurality of engaging protrusions 721a formed at the ends on the outer diameter side thereof are engaged with the spline protrusions 411a of the clutch drum 41, and are axially movable and relative to the clutch drum 41. It cannot rotate. In the inner clutch plate 722, a plurality of engaging protrusions 722a formed at the end on the inner diameter side thereof are engaged with the spline protrusions 62a of the large-diameter cylindrical portion 62 of the second output rotating member 6, and the second It is movable in the axial direction and cannot rotate relative to the output rotating member 6.

第１の受圧部材７３は、第１の出力回転部材５と一体に回転し、第１のピストン７５の押圧力を第１のクラッチ７１を介して受ける。第２の受圧部材７４は、第２の出力回転部材６と一体に回転し、第２のピストン７６の押圧力を第２のクラッチ７２を介して受ける。本実施の形態では、第１の受圧部材７３の内径端部が円盤部５１の外径端部に、また第２の受圧部材７４の内径端部が円盤部６１の外径端部に、それぞれ溶接により固定されている。なお、鍛造や切削により、第１の受圧部材７３と第１の出力回転部材５とを一体に成形してもよく、第２の受圧部材７４と第２の出力回転部材６とを一体に成形してもよい。 The first pressure receiving member 73 rotates integrally with the first output rotating member 5, and receives the pressing force of the first piston 75 via the first clutch 71. The second pressure receiving member 74 rotates integrally with the second output rotating member 6, and receives the pressing force of the second piston 76 via the second clutch 72. In the present embodiment, the inner diameter end of the first pressure receiving member 73 is on the outer diameter end of the disk portion 51, and the inner diameter end of the second pressure receiving member 74 is on the outer diameter end of the disk portion 61, respectively. It is fixed by welding. The first pressure receiving member 73 and the first output rotating member 5 may be integrally formed by forging or cutting, and the second pressure receiving member 74 and the second output rotating member 6 may be integrally formed. You may.

第１及び第２の受圧部材７３，７４は、回転軸線Ｏ２を中心とする円環板状の部材であり、クラッチドラム４１の円筒部４１１の内側に配置され、第１及び第２の出力回転部材５，６の円盤部５１，６１の径方向外側で軸方向に対向している。第１の受圧部材７３及び第２の受圧部材７４は、第１及び第２のクラッチ７１，７２を介して第１及び第２のピストン７５，７６の押圧力を受ける受面とは反対側の背面同士が向かい合わされている。第１の受圧部材７３の背面と第２の受圧部材７４の背面との間には軸方向の隙間Ｓ２が形成されている。隙間Ｓ１と隙間Ｓ２は回転軸線Ｏ２に直交する径方向に連続している。 First and second pressure receiving members 73 and 74 are annular plate-like member around the rotation axis O 2, is arranged inside the cylindrical portion 411 of the clutch drum 41, first and second output The discs 51 and 61 of the rotating members 5 and 6 are radially outside and face each other in the axial direction. The first pressure receiving member 73 and the second pressure receiving member 74 are on the side opposite to the receiving surface that receives the pressing force of the first and second pistons 75 and 76 via the first and second clutches 71 and 72. The backs are facing each other. The axial clearance S 2 is formed between the back surface of the back and the second pressure receiving member 74 of the first pressure receiving member 73. The gap S 1 and the gap S 2 are continuous in the radial direction orthogonal to the rotation axis O 2.

第１のピストン７５は、第３ケーシング３３に形成されたシリンダ３３１に軸方向の一部が収容された環状の押圧部材であり、その外周面及び内周面にＯリング７５１，７５２が嵌着されている。シリンダ３３１は、第３ケーシング３３に形成された第１油路３０１を介して油圧ユニット９から作動油が供給される。第１のピストン７５は、シリンダ３３１の油圧を受け、軸受８８を介して第１のクラッチ７１を第１の受圧部材７３に向かって軸方向に押圧する。第１のクラッチ７１は、第１のピストン７５の押圧力によって複数のアウタクラッチプレート７１１とインナクラッチプレート７１２とが摩擦接触し、入力回転部材４から第１の出力回転部材５に駆動力を伝達する。第１のクラッチ７１によって伝達される駆動力は、シリンダ３３１に供給される作動油の油圧が高いほど大きくなる。 The first piston 75 is an annular pressing member in which a part in the axial direction is housed in a cylinder 331 formed in the third casing 33, and O-rings 751 and 752 are fitted on the outer peripheral surface and the inner peripheral surface thereof. Has been done. The cylinder 331 is supplied with hydraulic oil from the hydraulic unit 9 via the first oil passage 301 formed in the third casing 33. The first piston 75 receives the flood pressure of the cylinder 331 and presses the first clutch 71 axially toward the first pressure receiving member 73 via the bearing 88. In the first clutch 71, a plurality of outer clutch plates 711 and inner clutch plates 712 are in frictional contact with each other due to the pressing force of the first piston 75, and a driving force is transmitted from the input rotating member 4 to the first output rotating member 5. To do. The driving force transmitted by the first clutch 71 increases as the oil pressure of the hydraulic oil supplied to the cylinder 331 increases.

第２のピストン７６は、第２ケーシング３２に形成されたシリンダ３２１に軸方向の一部が収容された環状の押圧部材であり、その外周面及び内周面にＯリング７６１，７６２が嵌着されている。シリンダ３２１は、第３ケーシング３３及び第２ケーシング３２に形成された第２油路３０２を介して油圧ユニット９から作動油が供給される。第２のピストン７６は、シリンダ３２１の油圧を受け、軸受８９及び中継部材７７を介して第２のクラッチ７２を第２の受圧部材７４に向かって軸方向に押圧する。第２のクラッチ７２は、第２のピストン７６の押圧力によって複数のアウタクラッチプレート７２１とインナクラッチプレート７２２とが摩擦接触し、入力回転部材４から第２の出力回転部材６に駆動力を伝達する。第２のクラッチ７２によって伝達される駆動力は、シリンダ３２１に供給される作動油の油圧が高いほど大きくなる。 The second piston 76 is an annular pressing member in which a part in the axial direction is housed in a cylinder 321 formed in the second casing 32, and O-rings 761 and 762 are fitted on the outer peripheral surface and the inner peripheral surface thereof. Has been done. The cylinder 321 is supplied with hydraulic oil from the hydraulic unit 9 via the second oil passage 302 formed in the third casing 33 and the second casing 32. The second piston 76 receives the flood pressure of the cylinder 321 and presses the second clutch 72 axially toward the second pressure receiving member 74 via the bearing 89 and the relay member 77. In the second clutch 72, the plurality of outer clutch plates 721 and the inner clutch plate 722 are in frictional contact with each other due to the pressing force of the second piston 76, and the driving force is transmitted from the input rotating member 4 to the second output rotating member 6. To do. The driving force transmitted by the second clutch 72 increases as the oil pressure of the hydraulic oil supplied to the cylinder 321 increases.

中継部材７７は、クラッチドラム４１の底部４１２と第２のクラッチ７２との間に配置された円環部７７１と、円環部７７１から軸方向に突出した複数の突部７７２とを一体に有し、第２のピストン７６の押圧力を軸受８９から第２のクラッチ７２に中継して伝達する。中継部材７７は、複数の突部７７２が底部４１２に形成された複数の貫通孔４１２ａに挿入され、入力回転部材４と共に回転する。中継部材７７には、例えば６つの突部７７２が、円環部７７１の周方向に沿って等間隔をもって形成されている。 The relay member 77 integrally includes an annular portion 771 arranged between the bottom portion 412 of the clutch drum 41 and the second clutch 72, and a plurality of protrusions 772 protruding in the axial direction from the annular portion 771. Then, the pressing force of the second piston 76 is relayed from the bearing 89 to the second clutch 72 and transmitted. The relay member 77 has a plurality of protrusions 772 inserted into a plurality of through holes 412a formed in the bottom portion 412, and rotates together with the input rotating member 4. In the relay member 77, for example, six protrusions 772 are formed at equal intervals along the circumferential direction of the annular portion 771.

シリンダ３２１，３３１には、油圧ユニット９から作動油が供給される。軸受８８，８９は、スラスト針状ころ軸受であり、第１及び第２のピストン７５，７６に係合して径方向に位置決めされている。第１及び第２のクラッチ７１，７２及び軸受８０〜８９は、第２ケーシング３２の第２収容空間３２０に封入された潤滑油によって潤滑される。 Hydraulic oil is supplied to the cylinders 321 and 331 from the hydraulic unit 9. Bearings 88 and 89 are thrust needle roller bearings, which are engaged with the first and second pistons 75 and 76 and are positioned in the radial direction. The first and second clutches 71 and 72 and the bearings 80 to 89 are lubricated by the lubricating oil sealed in the second accommodation space 320 of the second casing 32.

軸受８５は、第２の出力回転部材６を入力回転部材４の筒体４２に対して回転可能に支持している。軸受８６は、第１の出力回転部材５をケース部材３の第３ケーシング３３に対して回転可能に支持している。軸受８５及び軸受８６は、外輪８５１，８６１と内輪８５２，８６２との間に複数の円錐ころ８５３，８６３が配置された円錐ころ軸受である。軸受８５は、円錐ころ８５３の大径側の端部が第２の出力回転部材６の円盤部６１側となるように配置されている。軸受８６は、円錐ころ８６３の大径側の端部が第１の出力回転部材５の円盤部５１側となるように配置されている。 The bearing 85 rotatably supports the second output rotating member 6 with respect to the tubular body 42 of the input rotating member 4. The bearing 86 rotatably supports the first output rotating member 5 with respect to the third casing 33 of the case member 3. The bearing 85 and the bearing 86 are conical roller bearings in which a plurality of conical rollers 853 and 863 are arranged between the outer rings 851 and 861 and the inner rings 852 and 862. The bearing 85 is arranged so that the end portion of the conical roller 853 on the large diameter side is on the disk portion 61 side of the second output rotating member 6. The bearing 86 is arranged so that the end portion of the conical roller 863 on the large diameter side is on the disk portion 51 side of the first output rotating member 5.

軸受８５は、外輪８５１が筒体４２の支持筒部４２２の内側に配置され、内輪８５２が第２の出力回転部材６の小径円筒部６３の外側に配置されている。また、軸受８５は、外輪８５１の軸方向一端面が支持筒部４２２に形成された段差面４２２ａに当接し、かつ内輪８５２の軸方向一端面が第２の出力回転部材６の円盤部６１に当接して、軸方向への移動が規制されている。 In the bearing 85, the outer ring 851 is arranged inside the support cylinder portion 422 of the cylinder body 42, and the inner ring 852 is arranged outside the small diameter cylindrical portion 63 of the second output rotating member 6. Further, in the bearing 85, the axial end surface of the outer ring 851 is in contact with the stepped surface 422a formed on the support cylinder portion 422, and the axial end surface of the inner ring 852 is attached to the disk portion 61 of the second output rotating member 6. Axial movement is restricted by contact.

軸受８６は、外輪８６１が第３ケーシング３３に設けられた環状突起３３２の内側に配置され、内輪８６２が第１の出力回転部材６の小径円筒部５３の外側に配置されている。環状突起３３２は、第１の出力回転部材５の大径円筒部５２の内側に設けられ、環状突起３３２の外周面が大径円筒部５２の内周面に対向している。軸受８６は、外輪８６１の軸方向一端面が環状突起３３２に形成された段差面３３２ａに当接し、かつ内輪８６２の軸方向一端面がシム７８に当接して、軸方向移動が規制されている。シム７８は、内輪８６２の軸方向一端面と小径円筒部５３に形成された段差面５３ｂとの間に配置されている。 In the bearing 86, the outer ring 861 is arranged inside the annular projection 332 provided on the third casing 33, and the inner ring 862 is arranged outside the small-diameter cylindrical portion 53 of the first output rotating member 6. The annular projection 332 is provided inside the large-diameter cylindrical portion 52 of the first output rotating member 5, and the outer peripheral surface of the annular projection 332 faces the inner peripheral surface of the large-diameter cylindrical portion 52. In the bearing 86, one end surface in the axial direction of the outer ring 861 abuts on the stepped surface 332a formed on the annular projection 332, and one end surface in the axial direction of the inner ring 862 abuts on the shim 78, so that the axial movement is restricted. .. The shim 78 is arranged between one end surface of the inner ring 862 in the axial direction and a stepped surface 53b formed on the small-diameter cylindrical portion 53.

軸受８５，８６は、軸方向に予圧されており、シム７８によってこの予圧が調整されている。シム７８は、軸方向に所定の厚みを有する円環板状の予圧調整部材であり、駆動力伝達装置２の製造工程において、入力回転部材４の筒体４２や第１及び第２の出力回転部材５，６の寸法測定結果に基づいて選択された厚みのものが用いられている。このシム７８による予圧の調整により、入力回転部材４ならびに第及び第２の出力回転部材５，６が軸方向にガタつくことなく、かつ円滑に回転可能となっている。 The bearings 85 and 86 are preloaded in the axial direction, and this preload is adjusted by the shim 78. The shim 78 is an annular plate-shaped preload adjusting member having a predetermined thickness in the axial direction, and in the manufacturing process of the driving force transmission device 2, the cylinder 42 of the input rotating member 4 and the first and second output rotations. Those having a thickness selected based on the dimensional measurement results of the members 5 and 6 are used. By adjusting the preload by the shim 78, the input rotating member 4 and the second and second output rotating members 5 and 6 can rotate smoothly without rattling in the axial direction.

軸受８７は、第１の出力回転部材５及び第２の出力回転部材６の軸方向の間に配置されている。より具体的には、第１の出力回転部材５の円盤部５１と第２の出力回転部材６の円盤部６１との間に軸受８７が配置されており、軸受８７によって隙間Ｓ１，Ｓ２が保持されている。本実施の形態では、第１の出力回転部材５の円盤部５１に軸方向に開口する環状の凹部５１０が形成されており、この凹部５１０に軸受８７の一部が収容されている。 The bearing 87 is arranged between the first output rotating member 5 and the second output rotating member 6 in the axial direction. More specifically, the disc portion 51 of the first output rotary member 5 bearing 87 is disposed between the disk portion 61 of the second output rotary member 6, a gap S 1 by a bearing 87, S 2 Is held. In the present embodiment, the disk portion 51 of the first output rotating member 5 is formed with an annular recess 510 that opens in the axial direction, and a part of the bearing 87 is housed in the recess 510.

軸受８７は、スラスト針状ころ軸受であり、インナレース８７１及びアウタレース８７２と、インナレース８７１とアウタレース８７２との間に配置された複数のころ８７３とを有している。インナレース８７１は、凹部５１０の底面に当接し、アウタレース８７２は、第２の出力回転部材６の円盤部６１に当接している。軸受８７は、第１及び第２のクラッチ７１，７２よりも小径であり、より具体的にはアウタレース８７２の外径がインナクラッチプレート７１２，７２２の内径よりも小さい。 The bearing 87 is a thrust needle roller bearing and has an inner race 871 and an outer race 872, and a plurality of rollers 873 arranged between the inner race 871 and the outer race 872. The inner race 871 is in contact with the bottom surface of the recess 510, and the outer race 872 is in contact with the disk portion 61 of the second output rotating member 6. The bearing 87 has a smaller diameter than the first and second clutches 71 and 72, and more specifically, the outer diameter of the outer race 872 is smaller than the inner diameter of the inner clutch plates 712 and 722.

軸受８４，８５，８６，８７は、本発明の第１乃至第４の軸受にそれぞれ相当する。本実施の形態では、軸受８４〜８７による軸受構造によって、第１及び第２のピストン７５，７６の押圧力を受けながら、第１の受圧部材７３と第２の受圧部材７４とを接触させることなく、入力回転部材４ならびに第１及び第２の出力回転部材５，６をケース部材３の内部で円滑に回転可能としている。 Bearings 84, 85, 86, and 87 correspond to the first to fourth bearings of the present invention, respectively. In the present embodiment, the first pressure receiving member 73 and the second pressure receiving member 74 are brought into contact with each other while receiving the pressing force of the first and second pistons 75 and 76 by the bearing structure of the bearings 84 to 87. Instead, the input rotating member 4 and the first and second output rotating members 5 and 6 can be smoothly rotated inside the case member 3.

（油圧ユニット９の構成）
図４は、油圧ユニット９の構成例を模式的に示す構成図である。油圧ユニット９は、制御装置１０から供給される電流に応じたトルクを発生する電動モータ９１と、電動モータ９１に連結軸９２によって連結された油圧ポンプ９３と、リリーフ弁９４と、第１及び第２の制御弁９５，９６とを有している。電動モータ９１は、第３ケーシング３３に取り付けられ、油圧ポンプ９３、リリーフ弁９４、ならびに第１及び第２の制御弁９５，９６は、第２ケーシング３２に形成された収容室３２２（図２参照）に収容されている。図２では、リリーフ弁９４ならびに第１及び第２の制御弁９５，９６の手前に配置された油圧ポンプ９３を図示している。 (Structure of hydraulic unit 9)
FIG. 4 is a configuration diagram schematically showing a configuration example of the hydraulic unit 9. The hydraulic unit 9 includes an electric motor 91 that generates torque according to a current supplied from the control device 10, a hydraulic pump 93 that is connected to the electric motor 91 by a connecting shaft 92, a relief valve 94, and first and first. It has two control valves 95 and 96. The electric motor 91 is attached to the third casing 33, and the hydraulic pump 93, the relief valve 94, and the first and second control valves 95 and 96 are housed chambers 322 formed in the second casing 32 (see FIG. 2). ). FIG. 2 illustrates the relief valve 94 and the hydraulic pump 93 arranged in front of the first and second control valves 95 and 96.

電動モータ９１は、例えばＤＣブラシレスモータである。油圧ポンプ９３は、連結軸９２の回転数に応じた量の作動油をリザーバ９０から汲み上げて吐出する。油圧ポンプ９３としては、例えば外接ギヤポンプや内接ギヤポンプ、あるいはベーンポンプを用いることができる。リリーフ弁９４は、吐出された作動油の一部をリザーバ９０に還流させる固定絞り弁である。 The electric motor 91 is, for example, a DC brushless motor. The hydraulic pump 93 pumps and discharges an amount of hydraulic oil corresponding to the rotation speed of the connecting shaft 92 from the reservoir 90. As the hydraulic pump 93, for example, an external gear pump, an internal gear pump, or a vane pump can be used. The relief valve 94 is a fixed throttle valve that allows a part of the discharged hydraulic oil to return to the reservoir 90.

第１の制御弁９５は、油圧ポンプ９３から第１油路３０１を経てシリンダ３３１に至る経路に配置されている。第２の制御弁９６は、油圧ポンプ９３から第２油路３０２を経てシリンダ３２１に至る経路に配置されている。第１及び第２の制御弁９５，９６は、シリンダ３２１，３３１に供給される作動油の圧力を調節する圧力制御弁であり、その弁開度が制御装置１０から供給される電流に応じて変化する。制御装置１０は、油圧ポンプ９３の吐出圧がシリンダ３２１，３３１のそれぞれに供給すべき作動油の油圧よりも高くなるように電動モータ９１を制御する。 The first control valve 95 is arranged in a path from the hydraulic pump 93 to the cylinder 331 via the first oil passage 301. The second control valve 96 is arranged in a path from the hydraulic pump 93 to the cylinder 321 via the second oil passage 302. The first and second control valves 95 and 96 are pressure control valves that adjust the pressure of the hydraulic oil supplied to the cylinders 321 and 331, and the valve opening degree thereof depends on the current supplied from the control device 10. Change. The control device 10 controls the electric motor 91 so that the discharge pressure of the hydraulic pump 93 becomes higher than the hydraulic pressure of the hydraulic oil to be supplied to each of the cylinders 321 and 331.

（軸受８４〜８７による軸受構造の作用）
図５（ａ）は、シリンダ３３１に作動油が供給され、第１のピストン７５が押圧力を発生する際の押圧力の受け構造を示す説明図である。図５（ａ）では、第１のピストン７５の押圧力の流れを太線で示している。 (Action of bearing structure by bearings 84 to 87)
FIG. 5A is an explanatory view showing a structure for receiving the pressing force when the hydraulic oil is supplied to the cylinder 331 and the first piston 75 generates the pressing force. In FIG. 5A, the flow of the pressing force of the first piston 75 is shown by a thick line.

シリンダ３３１に油圧ユニット９から作動油が供給されると、第１のピストン７５が第１のクラッチ７１を第１の受圧部材７３に向かって押圧し、第１のピストン７５の押圧力が第１の受圧部材７３から第１の出力回転部材５の円盤部５１に伝達される。第１の出力回転部材５の円盤部５１に伝達された押圧力は、軸受８７、第２の出力回転部材６の円盤部６１、軸受８５、筒体４２の支持筒部４２２及び基部４２３、ならびに軸受８４を経て第２ケーシング３２の受面３２ａに伝達される。つまり、第１の軸受としての軸受８４及び第２の軸受としての軸受８５が、第１のピストン７５の押圧力を、第４の軸受としての軸受８７及び第２の出力回転部材６を介して受ける。 When hydraulic oil is supplied to the cylinder 331 from the hydraulic unit 9, the first piston 75 presses the first clutch 71 toward the first pressure receiving member 73, and the pressing force of the first piston 75 is the first. It is transmitted from the pressure receiving member 73 of the above to the disk portion 51 of the first output rotating member 5. The pressing force transmitted to the disk portion 51 of the first output rotating member 5 is the bearing 87, the disk portion 61 of the second output rotating member 6, the bearing 85, the support tubular portion 422 and the base portion 423 of the tubular body 42, and the base portion 423. It is transmitted to the receiving surface 32a of the second casing 32 via the bearing 84. That is, the bearing 84 as the first bearing and the bearing 85 as the second bearing apply the pressing force of the first piston 75 via the bearing 87 as the fourth bearing and the second output rotating member 6. receive.

図５（ｂ）は、シリンダ３２１に作動油が供給され、第２のピストン７６が押圧力を発生する際の押圧力の受け構造を示す説明図である。図５（ｂ）では、第２のピストン７６の押圧力の流れを太線で示している。 FIG. 5B is an explanatory view showing a structure for receiving the pressing force when the hydraulic oil is supplied to the cylinder 321 and the second piston 76 generates the pressing force. In FIG. 5B, the flow of the pressing force of the second piston 76 is shown by a thick line.

シリンダ３２１に油圧ユニット９から作動油が供給されると、第２のピストン７６が第２のクラッチ７２を第２の受圧部材７４に向かって押圧し、第２のピストン７６の押圧力が第２の受圧部材７４から第２の出力回転部材６に伝達される。第２の出力回転部材６に伝達された押圧力は、軸受８７、第１の出力回転部材５の円盤部５１及び小径円筒部５３、シム７８、ならびに軸受８６を経て第３ケーシング３３の環状突起３３２に形成された段差面３３２ａに伝達される。つまり、第３の軸受としての軸受８６が、第２のピストン７６の押圧力を、第４の軸受としての軸受８７及び第１の出力回転部材５を介して受ける。 When hydraulic oil is supplied to the cylinder 321 from the hydraulic unit 9, the second piston 76 presses the second clutch 72 toward the second pressure receiving member 74, and the pressing force of the second piston 76 is the second. It is transmitted from the pressure receiving member 74 of the above to the second output rotating member 6. The pressing force transmitted to the second output rotating member 6 passes through the bearing 87, the disk portion 51 and the small diameter cylindrical portion 53 of the first output rotating member 5, the shim 78, and the bearing 86, and the annular projection of the third casing 33. It is transmitted to the stepped surface 332a formed on the 332. That is, the bearing 86 as the third bearing receives the pressing force of the second piston 76 via the bearing 87 as the fourth bearing and the first output rotating member 5.

このように、軸受８７は、第１のピストン７５の押圧力を第２の出力回転部材６に伝達すると共に、第２のピストン７６の押圧力を第１の出力回転部材５に伝達する。また、軸受８６は、軸方向に予圧されているので、第２のピストン７６の押圧力を第１及び第２の出力回転部材５，６及び軸受８７を介して受けると共に、ケース部材３に対する第１の出力回転部材５の径方向への移動を規制することが可能である。これにより、第１の出力回転部材５がドライブシャフト１０７Ｌから径方向の力を受けても、この径方向の力が軸受８６によって受け止められ、第１の出力回転部材５がガタついて振動してしまうことがない。 In this way, the bearing 87 transmits the pressing force of the first piston 75 to the second output rotating member 6 and the pressing force of the second piston 76 to the first output rotating member 5. Further, since the bearing 86 is preloaded in the axial direction, the pressing force of the second piston 76 is received via the first and second output rotating members 5 and 6 and the bearing 87, and the third piston 76 is subjected to the pressing force with respect to the case member 3. It is possible to restrict the movement of the output rotating member 5 of 1 in the radial direction. As a result, even if the first output rotating member 5 receives a radial force from the drive shaft 107L, the radial force is received by the bearing 86, and the first output rotating member 5 rattles and vibrates. Never.

同様に、軸受８５は、軸方向に予圧されているので、第１のピストン７５の押圧力を第１及び第２の出力回転部材５，６及び軸受８７を介して受けると共に、ケース部材３に対する第２の出力回転部材６の径方向への移動を規制することが可能である。これにより、第２の出力回転部材６が、ドライブシャフト１０７Ｒに連結された連結シャフト２３を介してから径方向の力を受けても、この径方向の力が軸受８５によって受け止められ、第２の出力回転部材６がガタついて振動してしまうことがない。 Similarly, since the bearing 85 is preloaded in the axial direction, the pressing force of the first piston 75 is received via the first and second output rotating members 5 and 6 and the bearing 87, and the pressing force is applied to the case member 3. It is possible to restrict the radial movement of the second output rotating member 6. As a result, even if the second output rotating member 6 receives a radial force after passing through the connecting shaft 23 connected to the drive shaft 107R, this radial force is received by the bearing 85, and the second The output rotating member 6 does not rattle and vibrate.

なお、本実施の形態では、軸受８５，８７が円錐ころ軸受である場合について説明したが、軸受８５，８７を、外輪と内輪との間に複数の球状の転動体が配置された玉軸受により構成してもよい。この場合でも、軸受８５，８７を軸方向に予圧することで、上記の同様の効果を得ることができる。ただし、軸受８５，８７として円錐ころ軸受を用いれば、より確実に第１及び第２の出力回転部材５，６の振動を抑制しながら第１及び第２の出力回転部材５，６を円滑に回転させることができる。 In the present embodiment, the case where the bearings 85 and 87 are conical roller bearings has been described, but the bearings 85 and 87 are made of ball bearings in which a plurality of spherical rolling elements are arranged between the outer ring and the inner ring. It may be configured. Even in this case, the same effect as described above can be obtained by preloading the bearings 85 and 87 in the axial direction. However, if conical roller bearings are used as the bearings 85 and 87, the first and second output rotating members 5 and 6 can be smoothly suppressed while suppressing the vibrations of the first and second output rotating members 5 and 6 more reliably. Can be rotated.

（実施の形態の作用及び効果）
以上説明した本発明の実施の形態によれば、第１の受圧部材７３と第２の受圧部材７４との非接触状態、及び第１の出力回転部材５と第２の出力回転部材６が非接触状態が保たれるので、第１及び第２のクラッチ７１，７２が受ける押圧力が相互に干渉してしまうことを防ぐことが可能となる。また、例えば特許文献１に記載された駆動力伝達装置に比較して、少ない数の軸受で各回転部材を支持することができるので、コストを低減することが可能となる。 (Actions and effects of embodiments)
According to the embodiment of the present invention described above, the first pressure receiving member 73 and the second pressure receiving member 74 are not in contact with each other, and the first output rotating member 5 and the second output rotating member 6 are not in contact with each other. Since the contact state is maintained, it is possible to prevent the pressing forces received by the first and second clutches 71 and 72 from interfering with each other. Further, as compared with, for example, the driving force transmission device described in Patent Document 1, each rotating member can be supported by a smaller number of bearings, so that the cost can be reduced.

また、本実施の形態では、軸受８７が第１の出力回転部材５及び第２の出力回転部材６の軸方向の間に配置され、第１及び第２のクラッチ７１，７２よりも小径であるので、例えば軸受８７が第１及び第２のクラッチ７１，７２と軸方向に並んでいる場合に比較して、軸受８７のコストを低減することができる。またさらに、本実施の形態では、第１及び第２のピストン７５，７６の押圧力が中空ギヤシャフト２２に伝達しないので、リングギヤ２２１とピニオンギヤシャフト２１のギヤ部２１２との噛み合いが第１及び第２のピストン７５，７６の押圧力の影響を受けることなく良好に保たれる。 Further, in the present embodiment, the bearing 87 is arranged between the first output rotating member 5 and the second output rotating member 6 in the axial direction, and has a smaller diameter than the first and second clutches 71 and 72. Therefore, for example, the cost of the bearing 87 can be reduced as compared with the case where the bearing 87 is aligned with the first and second clutches 71 and 72 in the axial direction. Furthermore, in the present embodiment, since the pressing force of the first and second pistons 75 and 76 is not transmitted to the hollow gear shaft 22, the engagement between the ring gear 221 and the gear portion 212 of the pinion gear shaft 21 is the first and first. It is kept good without being affected by the pressing force of the pistons 75 and 76 of 2.

［変形例］
次に、本発明の実施の形態の変形例について、図６及び図７を参照して説明する。これらの変形例は、第１及び第２の受圧部材７３，７４の第１及び第２の出力回転部材５，６との連結構造ならびに軸受８７の配置が上記の実施の形態と異なる他は、上記の実施の形態と同様に構成されているので、この違いの部分について重点的に説明し、他の部分については重複した説明を省略する。 [Modification example]
Next, a modified example of the embodiment of the present invention will be described with reference to FIGS. 6 and 7. These modifications are different from the above-described embodiment except that the connection structure of the first and second pressure receiving members 73 and 74 with the first and second output rotating members 5 and 6 and the arrangement of the bearing 87 are different from those in the above embodiment. Since the configuration is the same as that of the above embodiment, the difference portion will be mainly described, and the duplicate description will be omitted for the other portions.

図６は、第１の変形例における第１及び第２の受圧部材７３，７４の周辺部を示す断面図である。図７は、第２の変形例における第１及び第２の受圧部材７３，７４の周辺部を示す断面図である。図６及び図７において、図３等を参照して説明したものと共通する構成要素については、同一の符号を付して詳細な説明を省略する。また、図６及び図７に示す部分以外の構成については図３を援用して説明する。 FIG. 6 is a cross-sectional view showing peripheral portions of the first and second pressure receiving members 73 and 74 in the first modification. FIG. 7 is a cross-sectional view showing peripheral portions of the first and second pressure receiving members 73 and 74 in the second modification. In FIGS. 6 and 7, components common to those described with reference to FIGS. 3 and the like are designated by the same reference numerals and detailed description thereof will be omitted. Further, the configurations other than the portions shown in FIGS. 6 and 7 will be described with reference to FIG.

上記の実施の形態では、軸受８７が第１の出力回転部材５と第２の出力回転部材６との間に配置された場合について説明したが、第１及び第２の変形例では、軸受８７が第１の受圧部材７３と第２の受圧部材７４との間に配置されている。より具体的には、第１の受圧部材７３において第１のピストン７５の押圧力を受ける受面７３ａとは反対側の背面７３ｂに軸方向に窪んだ環状の凹部７３０が形成されると共に、第２の受圧部材７４において第２のピストン７６の押圧力を受ける受面７４ａとは反対側の背面７４ｂに軸方向に窪んだ環状の凹部７４０が形成され、軸受８７が凹部７３０の底面７３０ａと凹部７４０の底面７４０ａとの間に配置されている。 In the above embodiment, the case where the bearing 87 is arranged between the first output rotating member 5 and the second output rotating member 6 has been described, but in the first and second modified examples, the bearing 87 has been described. Is arranged between the first pressure receiving member 73 and the second pressure receiving member 74. More specifically, in the first pressure receiving member 73, an annular recess 730 recessed in the axial direction is formed on the back surface 73b on the side opposite to the receiving surface 73a receiving the pressing force of the first piston 75, and the first In the pressure receiving member 74 of 2, an annular recess 740 recessed in the axial direction is formed on the back surface 74b opposite to the receiving surface 74a receiving the pressing force of the second piston 76, and the bearing 87 is recessed with the bottom surface 730a of the recess 730. It is arranged between the bottom surface of the 740 and the bottom surface of the 740a.

第１の変形例では、第１の受圧部材７３の内径側の端部に内周スプライン嵌合部７３１が設けられ、この内周スプライン嵌合部７３１が第１の出力回転部材５の円盤部５１の外径側の端部に設けられた外周スプライン嵌合部５１１に嵌合されている。第１の受圧部材７３は、第１の出力回転部材５との相対回転が規制され、第１の出力回転部材５と一体に回転する。また、第１の受圧部材７３は、第１の出力回転部材５に対し、第２のクラッチ７２側への軸方向移動が可能であり、第１のクラッチ７１側への軸方向移動は、円盤部５１に形成された段差面５１ａとの当接により規制されている。 In the first modification, an inner peripheral spline fitting portion 731 is provided at an end portion on the inner diameter side of the first pressure receiving member 73, and the inner peripheral spline fitting portion 731 is a disk portion of the first output rotating member 5. It is fitted to the outer peripheral spline fitting portion 511 provided at the end on the outer diameter side of 51. The first pressure receiving member 73 is restricted from rotating relative to the first output rotating member 5, and rotates integrally with the first output rotating member 5. Further, the first pressure receiving member 73 can move in the axial direction toward the second clutch 72 side with respect to the first output rotating member 5, and the axial movement toward the first clutch 71 side is a disk. It is regulated by contact with the stepped surface 51a formed on the portion 51.

同様に、第２の受圧部材７４には、内径側の端部に内周スプライン嵌合部７４１が設けられ、この内周スプライン嵌合部７４１が第２の出力回転部材６の円盤部６１の外径側の端部に設けられた外周スプライン嵌合部６１１に嵌合されている。第２の受圧部材７４は、第２の出力回転部材６との相対回転が規制され、第２の出力回転部材６と一体に回転する。また、第２の受圧部材７４は、第２の出力回転部材６に対し、第１のクラッチ７１側への軸方向移動が可能であり、第２のクラッチ７２側への軸方向移動は、円盤部６１に形成された段差面６１ａとの当接により規制されている。 Similarly, the second pressure receiving member 74 is provided with an inner peripheral spline fitting portion 741 at the end on the inner diameter side, and the inner peripheral spline fitting portion 741 is a disk portion 61 of the second output rotating member 6. It is fitted to the outer peripheral spline fitting portion 611 provided at the end on the outer diameter side. The second pressure receiving member 74 is restricted from rotating relative to the second output rotating member 6, and rotates integrally with the second output rotating member 6. Further, the second pressure receiving member 74 can move in the axial direction toward the first clutch 71 side with respect to the second output rotating member 6, and the axial movement toward the second clutch 72 side is a disk. It is regulated by the contact with the stepped surface 61a formed on the portion 61.

この第１の変形例において、第１の受圧部材７３が第１のピストン７５の押圧力を第１のクラッチ７１を介して受けると、この押圧力が軸受８７及び第２の受圧部材７４を介して第２の出力回転部材６に伝達され、軸受８５、筒体４２、及び軸受８４を介して第２ケーシング３２の受面３２ａに伝達される。また、第２の受圧部材７４が第２のピストン７６の押圧力を第２のクラッチ７２を介して受けると、この押圧力が軸受８７及び第１の受圧部材７３を介して第１の出力回転部材５に伝達され、シム７８及び軸受８６を介して第３ケーシング３３の環状突起３３２の段差面３３２ａに伝達される。これにより、上記の実施の形態と同様の効果が得られる。 In this first modification, when the first pressure receiving member 73 receives the pressing force of the first piston 75 via the first clutch 71, this pressing force is transmitted through the bearing 87 and the second pressure receiving member 74. It is transmitted to the second output rotating member 6, and is transmitted to the receiving surface 32a of the second casing 32 via the bearing 85, the tubular body 42, and the bearing 84. Further, when the second pressure receiving member 74 receives the pressing force of the second piston 76 via the second clutch 72, the pressing force is applied to the first output rotation via the bearing 87 and the first pressure receiving member 73. It is transmitted to the member 5, and is transmitted to the stepped surface 332a of the annular protrusion 332 of the third casing 33 via the shim 78 and the bearing 86. As a result, the same effect as that of the above embodiment can be obtained.

一方、第２の変形例では、第２の受圧部材７４と第２の出力回転部材６との連結構造が第１の変形例と共通しているが、第１の受圧部材７３は、その内径側の端部に環状突起７３２が設けられ、この環状突起７３２が溶接箇所Ｗにおいて第１の出力回転部材５に溶接により固定されている。これは、次に述べるように、製造時における組み立てのしやすさを考慮したものである。 On the other hand, in the second modification, the connecting structure of the second pressure receiving member 74 and the second output rotating member 6 is common to that of the first modification, but the first pressure receiving member 73 has an inner diameter thereof. An annular protrusion 732 is provided at the end on the side, and the annular protrusion 732 is fixed to the first output rotating member 5 by welding at the welded portion W. This takes into consideration the ease of assembly at the time of manufacture, as described below.

つまり、第２ケーシング３２の第２収容空間３２０における第３ケーシング３３側の開口から各部品を挿入して機構部２４の組み立てを行う場合、第１及び第２の出力回転部材５，６のうち奥側にあたる第２の出力回転部材６に予め第２の受圧部材７４が固定されていると、インナクラッチプレート７２２の係合突起７２２ａを第２の出力回転部材６の大径円筒部６２のスプライン突起６２ａに係合させる作業が難しくなる。また、第２収容空間３２０の開口側にあたる第１の出力回転部材５と第１の受圧部材７３が予め固定されておらず、これらを第１の変形例のように第２収容空間３２０内でスプライン嵌合させて相対回転不能に連結する場合には、このスプライン嵌合のための位置合わせが難しくなる。 That is, when the mechanical portion 24 is assembled by inserting each component from the opening on the third casing 33 side in the second accommodating space 320 of the second casing 32, of the first and second output rotating members 5 and 6. When the second pressure receiving member 74 is fixed to the second output rotating member 6 on the back side in advance, the engaging projection 722a of the inner clutch plate 722 is spun line of the large diameter cylindrical portion 62 of the second output rotating member 6. The work of engaging with the protrusion 62a becomes difficult. Further, the first output rotating member 5 and the first pressure receiving member 73, which correspond to the opening side of the second accommodating space 320, are not fixed in advance, and these are placed in the second accommodating space 320 as in the first modification. When the splines are fitted and connected so that they cannot rotate relative to each other, the alignment for the spline fitting becomes difficult.

このように、第２の変形例によれば、第１及び第２の受圧部材７３，７４のうち、第２収容空間３２０の奥側にあたる第２の受圧部材７４が対応する第２の出力回転部材６に固定され、第２収容空間３２０の開口側にあたる第１の受圧部材７３が対応する第１の出力回転部材５に固定されていないので、第２ケーシング３２の開口から各部品を挿入し、第２収容空間３２０内で機構部２４の組み立てを行う製造方法を採用する場合に、機構部２４の組み立てが容易となる。 As described above, according to the second modification, of the first and second pressure receiving members 73 and 74, the second pressure receiving member 74 corresponding to the inner side of the second accommodating space 320 corresponds to the second output rotation. Since the first pressure receiving member 73 fixed to the member 6 and corresponding to the opening side of the second accommodating space 320 is not fixed to the corresponding first output rotating member 5, each component is inserted through the opening of the second casing 32. When the manufacturing method of assembling the mechanical portion 24 in the second accommodating space 320 is adopted, the mechanical portion 24 can be easily assembled.

なお、治具等の工夫により、他の組み立て方法を採用する場合でも機構部２４の組み立てを行うことができるが、第１及び第２の受圧部材７３，７４のうち少なくとも何れかを対応する第１及び第２の出力回転部材５，６のうち対応する出力回転部材に固定せず、スプライン嵌合により相対回転不能かつ軸方向に相対移動可能に連結することで、機構部２４の組み立てを容易にすることが可能である。すなわち、第２の変形例によれば、上記の実施の形態と同様の効果が得られると共に、機構部２４の組み立てを容易に行うことが可能となる。 The mechanism unit 24 can be assembled even when another assembling method is adopted by devising a jig or the like, but at least one of the first and second pressure receiving members 73 and 74 is supported. The mechanism unit 24 can be easily assembled by connecting the first and second output rotating members 5 and 6 so as not to be fixed to the corresponding output rotating members but to be relatively non-rotatable and axially movable by spline fitting. It is possible to. That is, according to the second modification, the same effect as that of the above-described embodiment can be obtained, and the mechanical portion 24 can be easily assembled.

（付記）
以上、本発明を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、実施の形態の中で説明した特徴の組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。 (Additional note)
Although the present invention has been described above based on the 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 the embodiments are essential to the means for solving the problems of the invention.

また、本発明は、その趣旨を逸脱しない範囲で適宜変形して実施することが可能である。例えば、上記の実施の形態では、第１及び第２の押圧部材としてのピストン７５，７６が油圧によって押圧力を発生する場合について説明したが、これに限らず、例えば電動モータの回転力がカム機構により変換された軸方向のカム推力により、第１及び第２の押圧部材が第１及び第２のクラッチ７１，７２を押圧するようにしてもよい。 In addition, the present invention can be appropriately modified and implemented without departing from the spirit of the present invention. For example, in the above embodiment, the case where the pistons 75 and 76 as the first and second pressing members generate the pressing force by the flood control has been described, but the present invention is not limited to this, and for example, the rotational force of the electric motor is a cam. The first and second pressing members may press the first and second clutches 71 and 72 by the axial cam thrust converted by the mechanism.

２…駆動力伝達装置 ３…ケース部材
４…入力回転部材 ５…第１の出力回転部材
６…第２の出力回転部材 ７１…第１のクラッチ
７２…第２のクラッチ ７３…第１の受圧部材
７４…第２の受圧部材 ７５…第１のピストン（第１の押圧部材）
７６…第２のピストン（第２の押圧部材） ８４…第１の軸受
８５…第２の軸受 ８６…第３の軸受
８７…第４の軸受 2 ... Driving force transmission device 3 ... Case member 4 ... Input rotating member 5 ... First output rotating member 6 ... Second output rotating member 71 ... First clutch 72 ... Second clutch 73 ... First pressure receiving member 74 ... Second pressure receiving member 75 ... First piston (first pressing member)
76 ... 2nd piston (second pressing member) 84 ... 1st bearing 85 ... 2nd bearing 86 ... 3rd bearing 87 ... 4th bearing

Claims (7)

入力回転部材に入力された駆動力を前記入力回転部材と同軸配置された第１及び第２の出力回転部材から出力する駆動力伝達装置であって、
前記入力回転部材ならびに前記第１及び第２の出力回転部材を収容するケース部材と、
前記入力回転部材と前記第１の出力回転部材との間に配置され、前記第１の出力回転部材に駆動力を伝達する第１のクラッチと、
前記入力回転部材と前記第２の出力回転部材との間に配置され、前記第２の出力回転部材に駆動力を伝達する第２のクラッチと、
前記第１のクラッチを軸方向に押圧する第１の押圧部材と、
前記第２のクラッチを軸方向に押圧する第２の押圧部材と、
前記第１の押圧部材の押圧力を前記第１のクラッチを介して受けると共に、前記第１の出力回転部材と一体に回転する第１の受圧部材と、
前記第２の押圧部材の押圧力を前記第２のクラッチを介して受けると共に、前記第２の出力回転部材と一体に回転する第２の受圧部材と、
前記ケース部材内に配置された複数の軸受と、を備え、
前記複数の軸受は、前記入力回転部材を前記ケース部材に対する軸方向移動を規制して支持する第１の軸受と、前記第２の出力回転部材を前記入力回転部材に対して支持する第２の軸受と、前記第１の出力回転部材を前記ケース部材に対して支持する第３の軸受と、前記第１及び第２の出力回転部材の軸方向の間もしくは前記第１及び第２の受圧部材の軸方向の間に配置された第４の軸受とを含み、
前記第１及び第２の軸受が前記第１の押圧部材の押圧力を前記第２の出力回転部材を介して受け、前記第３の軸受が前記第２の押圧部材の押圧力を前記第１の出力回転部材を介して受ける、
駆動力伝達装置。 A driving force transmission device that outputs the driving force input to the input rotating member from the first and second output rotating members coaxially arranged with the input rotating member.
A case member accommodating the input rotating member and the first and second output rotating members, and
A first clutch, which is arranged between the input rotating member and the first output rotating member and transmits a driving force to the first output rotating member,
A second clutch, which is arranged between the input rotating member and the second output rotating member and transmits a driving force to the second output rotating member,
A first pressing member that presses the first clutch in the axial direction,
A second pressing member that presses the second clutch in the axial direction,
A first pressure receiving member that receives the pressing force of the first pressing member via the first clutch and rotates integrally with the first output rotating member.
A second pressure receiving member that receives the pressing force of the second pressing member via the second clutch and rotates integrally with the second output rotating member.
With a plurality of bearings arranged in the case member,
The plurality of bearings include a first bearing that regulates the axial movement of the input rotating member with respect to the case member and supports the second output rotating member, and a second bearing that supports the second output rotating member with respect to the input rotating member. Between the bearing, the third bearing that supports the first output rotating member with respect to the case member, and the axial direction of the first and second output rotating members, or between the first and second pressure receiving members. Including a fourth bearing located between the axial directions of
The first and second bearings receive the pressing force of the first pressing member via the second output rotating member, and the third bearing receives the pressing force of the second pressing member. Received through the output rotating member of
Driving force transmission device. 前記第１及び第２の受圧部材は、前記第１及び第２の押圧部材の押圧力を受ける受面とは反対側の背面同士が向かい合わされ、当該背面間の軸方向の隙間が前記第４の軸受によって保持され、
前記第４の軸受は、前記第１の押圧部材の押圧力を前記第２の出力回転部材に伝達すると共に、前記第２の押圧部材の押圧力を前記第１の出力回転部材に伝達する、
請求項１に記載の駆動力伝達装置。 The back surfaces of the first and second pressure receiving members are opposed to each other on the side opposite to the receiving surfaces of the first and second pressing members, and the axial gap between the back surfaces is the fourth. Held by bearings
The fourth bearing transmits the pressing force of the first pressing member to the second output rotating member and also transmits the pressing force of the second pressing member to the first output rotating member.
The driving force transmission device according to claim 1. 前記第３の軸受は、前記第２の押圧部材の押圧力を前記第２の出力回転部材及び前記第４の軸受を介して受けると共に、前記ケース部材に対する前記第１の出力回転部材の径方向への移動を規制する、
請求項１又は２に記載の駆動力伝達装置。 The third bearing receives the pressing force of the second pressing member via the second output rotating member and the fourth bearing, and in the radial direction of the first output rotating member with respect to the case member. Regulate movement to,
The driving force transmission device according to claim 1 or 2. 前記第２及び第３の軸受は、軸方向に予圧された円錐ころ軸受である、
請求項３に記載の駆動力伝達装置。 The second and third bearings are axially preloaded tapered roller bearings.
The driving force transmission device according to claim 3. 前記第４の軸受は、前記第１及び第２の出力回転部材の軸方向の間に配置され、
前記第１の受圧部材が前記第１の出力回転部材に固定又は一体成形されると共に、前記第２の受圧部材が前記第２の出力回転部材に固定又は一体成形された、
請求項１乃至４の何れか１項に記載の駆動力伝達装置。 The fourth bearing is arranged between the axial directions of the first and second output rotating members.
The first pressure receiving member was fixed or integrally molded to the first output rotating member, and the second pressure receiving member was fixed or integrally molded to the second output rotating member.
The driving force transmission device according to any one of claims 1 to 4. 前記第４の軸受は、前記第１及び第２の受圧部材の軸方向の間に配置され、
前記第１及び第２の受圧部材は、少なくとも何れか一方の受圧部材が前記第１及び第２の出力回転部材のうち対応する出力回転部材に固定されていない、
請求項１乃至４の何れか１項に記載の駆動力伝達装置。 The fourth bearing is arranged between the axial directions of the first and second pressure receiving members.
In the first and second pressure receiving members, at least one of the pressure receiving members is not fixed to the corresponding output rotating member of the first and second output rotating members.
The driving force transmission device according to any one of claims 1 to 4. 前記第４の軸受は、前記第１及び第２の受圧部材の軸方向の間に配置され、
前記第１及び第２の受圧部材のうち、一方の受圧部材が前記第１及び第２の出力回転部材のうち対応する出力回転部材に固定され、他方の受圧部材が前記第１及び第２の出力回転部材のうち対応する出力回転部材に固定されていない、
請求項１乃至４の何れか１項に記載の駆動力伝達装置。 The fourth bearing is arranged between the axial directions of the first and second pressure receiving members.
Of the first and second pressure receiving members, one pressure receiving member is fixed to the corresponding output rotating member of the first and second output rotating members, and the other pressure receiving member is the first and second output rotating members. Of the output rotating members, they are not fixed to the corresponding output rotating members,
The driving force transmission device according to any one of claims 1 to 4.
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JP5394486B2 (en) * 2010-01-25 2014-01-22 本田技研工業株式会社 Power transmission device
FR3025272B1 (en) * 2014-09-03 2018-03-02 Valeo Embrayages DUAL WET CLUTCH MECHANISM FOR A TRANSMISSION SYSTEM

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