JP6260367B2 - Clutch device - Google Patents

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JP6260367B2
JP6260367B2 JP2014047495A JP2014047495A JP6260367B2 JP 6260367 B2 JP6260367 B2 JP 6260367B2 JP 2014047495 A JP2014047495 A JP 2014047495A JP 2014047495 A JP2014047495 A JP 2014047495A JP 6260367 B2 JP6260367 B2 JP 6260367B2
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cam
clutch device
recess
connecting member
pressing
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JP2015172380A (en
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則行 藤井
則行 藤井
鈴木　邦彦
邦彦 鈴木
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JTEKT Corp
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Description

本発明は、部材間を係脱可能に連結するクラッチ装置に関する。   The present invention relates to a clutch device that removably connects members.

従来、例えば車両における一対の部材間を連結するクラッチ装置として、特許文献１に記載の電磁クラッチが知られている。   Conventionally, for example, an electromagnetic clutch described in Patent Document 1 is known as a clutch device that connects a pair of members in a vehicle.

この特許文献１に記載の電磁クラッチは、電磁アクチュエータと、互いに噛合わされる一対のドグ歯とを備えている。一対のドグ歯のうち、一方のドグ歯は車体に固定されたケースに対して相対回転不能かつ軸方向移動可能に支持され、他方のドグ歯は回転部材（遊星歯車機構のサンギヤ）に固定されている。それぞれのドグ歯には、噛み合いのための複数の噛み合い歯が形成されている。一方のドグ歯が他方のドグ歯に噛み合うと、回転部材が一方のドグ歯を介して固定部としての他方のドグ歯に連結され、その回転が規制される。   The electromagnetic clutch described in Patent Document 1 includes an electromagnetic actuator and a pair of dog teeth meshed with each other. Of the pair of dog teeth, one dog tooth is supported so that it cannot rotate relative to the case fixed to the vehicle body and can move in the axial direction, and the other dog tooth is fixed to the rotating member (sun gear of the planetary gear mechanism). ing. Each dog tooth is formed with a plurality of meshing teeth for meshing. When one dog tooth meshes with the other dog tooth, the rotating member is connected to the other dog tooth as the fixing portion via the one dog tooth, and the rotation is restricted.

電磁アクチュエータは、制御装置から供給される電流によって磁力を発生させる電磁コイルと、電磁コイルを保持するヨークと、電磁コイルの磁力によって軸方向に移動するプランジャと、プランジャを元の位置に復帰させる復帰バネとを有している。プランジャは、電磁コイルへ通電された際、一方のドグ歯を他方のドグ歯に噛み合わせるように移動させる。また、電磁コイルへの通電が遮断されると、復帰バネのバネ力によってプランジャが元の位置に戻り、一対のドグ歯の噛み合いが解除される。一対のドグ歯の噛み合いを維持する保持状態では、プランジャを移動させる際の電流値よりも小さい保持電流値の電流が電磁コイルに供給される。   The electromagnetic actuator includes an electromagnetic coil that generates a magnetic force by a current supplied from a control device, a yoke that holds the electromagnetic coil, a plunger that moves in an axial direction by the magnetic force of the electromagnetic coil, and a return that returns the plunger to its original position. And a spring. When the electromagnetic coil is energized, the plunger moves so that one dog tooth meshes with the other dog tooth. When the energization of the electromagnetic coil is interrupted, the plunger returns to the original position by the spring force of the return spring, and the engagement of the pair of dog teeth is released. In the holding state in which the engagement of the pair of dog teeth is maintained, a current having a holding current value smaller than the current value when the plunger is moved is supplied to the electromagnetic coil.

また、特許文献１に記載の電磁クラッチを制御する制御装置は、電磁コイルの温度を推定するコイル温度推定手段を有し、このコイル温度推定手段によって推定した電磁コイルの温度が正常な温度範囲から逸脱すると、電磁クラッチを過熱から保護するために電磁コイルへの電流供給を遮断し、電磁クラッチを解放する。   The control device for controlling the electromagnetic clutch described in Patent Document 1 has coil temperature estimation means for estimating the temperature of the electromagnetic coil, and the temperature of the electromagnetic coil estimated by the coil temperature estimation means is within a normal temperature range. When deviating, in order to protect the electromagnetic clutch from overheating, the current supply to the electromagnetic coil is cut off and the electromagnetic clutch is released.

特開２００９−２１０１１０号公報JP 2009-210110 A

特許文献１に記載の電磁クラッチでは、一対のドグ歯の噛み合いを維持するために、電磁コイルへの通電を継続する必要がある。このため、一対のドグ歯の噛み合い状態を維持する時間が長いと、電磁コイルでの消費電力量が大きくなると共に、電磁コイルの温度上昇を招来してしまう。前述のように、特許文献１に記載の電磁クラッチは、電磁コイルの温度が正常な温度範囲から逸脱すると制御装置からの電流供給が遮断されるため、長時間にわたって一対のドグ歯の噛み合いを維持することが困難となるおそれがある。   In the electromagnetic clutch described in Patent Document 1, it is necessary to continue energization of the electromagnetic coil in order to maintain the meshing of the pair of dog teeth. For this reason, if the time for maintaining the meshing state of the pair of dog teeth is long, the power consumption in the electromagnetic coil is increased and the temperature of the electromagnetic coil is increased. As described above, in the electromagnetic clutch described in Patent Document 1, when the temperature of the electromagnetic coil deviates from the normal temperature range, the current supply from the control device is cut off, so that the engagement of the pair of dog teeth is maintained for a long time. May be difficult to do.

そこで、本発明は、部材間の連結を維持する際に電磁コイルへの通電を必要とせず、もって消費電力量を削減することができ、長時間にわたって連結状態を維持することが可能なクラッチ装置を提供することを目的とする。   Therefore, the present invention does not require energization of the electromagnetic coil when maintaining the connection between the members, can reduce power consumption, and can maintain the connected state for a long time. The purpose is to provide.

本発明は、上記課題を解決するため、第１部材と第２部材とを係脱可能に連結するクラッチ装置であって、前記第１部材及び前記第２部材に係合して前記第１部材と前記第２部材とを連結する連結位置、及び前記第１部材と前記第２部材とを相対回転可能とする非連結位置の間を軸方向に進退移動する環状の連結部材と、前記連結部材を前記軸方向に押圧する押圧部材と、前記押圧部材を前記連結部材に対して相対回転させる回転力を付与する回転力付与機構とを備え、前記連結部材及び前記押圧部材のそれぞれの一部は、前記連結部材及び前記押圧部材のうち一方の部材に設けられたカム部と他方の部材に設けられた突起とからなるカム機構を構成し、前記カム部は、前記連結部材が前記非連結位置にあるときに前記突起の先端部が当接する第１凹部と、前記第１凹部に対して前記軸方向にずれた位置に形成され、前記連結部材が前記連結位置にあるときに前記突起の先端部が当接する第２凹部とを有し、回転力付与機構の作動によって前記連結部材と前記押圧部材とが相対回転し、前記突起の先端部が前記第１凹部と前記第２凹部との間に形成されたカム面を摺動することで、前記連結部材が前記連結位置と前記非連結位置との間を進退移動する、クラッチ装置を提供する。   In order to solve the above-mentioned problem, the present invention is a clutch device that releasably connects a first member and a second member, wherein the first member engages with the first member and the second member. A connecting position for connecting the first member and the second member; an annular connecting member that moves forward and backward in an axial direction between non-connecting positions that allow the first member and the second member to rotate relative to each other; and the connecting member A pressing member that presses the pressing member in the axial direction, and a rotational force applying mechanism that applies a rotational force that rotates the pressing member relative to the connecting member, and each of the connecting member and the pressing member includes: A cam mechanism comprising a cam portion provided on one member of the connecting member and the pressing member and a protrusion provided on the other member, wherein the connecting member is in the unconnected position. The tip of the projection abuts when A first recess, and a second recess formed at a position shifted in the axial direction with respect to the first recess, and a tip of the protrusion abuts when the connecting member is in the connecting position; By operating the rotational force applying mechanism, the connecting member and the pressing member are rotated relative to each other, and the tip of the protrusion slides on the cam surface formed between the first recess and the second recess. A clutch device is provided in which the connecting member moves forward and backward between the connecting position and the non-connecting position.

本発明によれば、部材間の連結を維持する際に電磁コイルへの通電を必要とせず、もって消費電力量を削減することができ、長時間にわたって連結状態を維持することが可能となる。   According to the present invention, it is not necessary to energize the electromagnetic coil when maintaining the connection between the members, so that the power consumption can be reduced, and the connected state can be maintained for a long time.

本発明の第１の実施の形態に係るクラッチ装置が搭載された四輪駆動車の概略構成図である。1 is a schematic configuration diagram of a four-wheel drive vehicle equipped with a clutch device according to a first embodiment of the present invention. クラッチ装置及びその周辺部の構成例を示す断面図である。It is sectional drawing which shows the structural example of a clutch apparatus and its peripheral part. 図２におけるクラッチ装置の要部拡大図である。It is a principal part enlarged view of the clutch apparatus in FIG. カム部の構成を模式的に説明する説明図であり、（ａ）は環状のカム部を平面上に展開した展開図、（ｂ）は（ａ）のＢ部拡大図である。It is explanatory drawing which illustrates the structure of a cam part typically, (a) is the expanded view which expand | deployed the cyclic | annular cam part on the plane, (b) is the B section enlarged view of (a). 本発明の第２の実施の形態に係るクラッチ装置の要部拡大図である。It is a principal part enlarged view of the clutch apparatus which concerns on the 2nd Embodiment of this invention. 第２の実施の形態に係るクラッチ装置の要部拡大図である。It is a principal part enlarged view of the clutch apparatus which concerns on 2nd Embodiment.

［第１の実施の形態］
以下、本発明の第１の実施の形態に係るクラッチ装置、及びこれを備えた四輪駆動車について、図面を参照しながら詳細に説明する。 [First Embodiment]
Hereinafter, a clutch device according to a first embodiment of the present invention and a four-wheel drive vehicle including the clutch device will be described in detail with reference to the drawings.

（四輪駆動車の全体構成）
図１は、本発明の実施の形態に係るクラッチ装置が搭載された四輪駆動車１の概略構成図である。四輪駆動車１は、駆動力伝達系１０、駆動源としてのエンジン１１、トランスミッション１２、主駆動輪としての前輪１３Ｌ，１３Ｒ、及び補助駆動輪としての後輪１４Ｌ，１４Ｒを備えている。なお、図１において、符号中の文字「Ｌ」は四輪駆動車１の前進方向に対する左側、文字「Ｒ」は四輪駆動車１の前進方向に対する右側の意味で使用している。 (Overall configuration of a four-wheel drive vehicle)
FIG. 1 is a schematic configuration diagram of a four-wheel drive vehicle 1 on which a clutch device according to an embodiment of the present invention is mounted. The four-wheel drive vehicle 1 includes a driving force transmission system 10, an engine 11 as a drive source, a transmission 12, front wheels 13L and 13R as main drive wheels, and rear wheels 14L and 14R as auxiliary drive wheels. In FIG. 1, the letter “L” in the code is used to mean the left side with respect to the forward direction of the four-wheel drive vehicle 1, and the letter “R” means the right side with respect to the forward direction of the four-wheel drive vehicle 1.

駆動力伝達系１０は、四輪駆動車１におけるトランスミッション１２から前輪１３Ｌ，１３Ｒ及び後輪１４Ｌ，１４Ｒ側に至る駆動力伝達経路にフロントディファレンシャル１５及びリヤディファレンシャル１６と共に配置されている。また、駆動力伝達系１０は、エンジン１１の駆動力（トルク）を前輪１３Ｌ，１３Ｒ側から後輪１４Ｌ，１４Ｒ側に伝達するプロペラシャフト１７と、プロペラシャフト１７よりも駆動力伝達経路の上流側でエンジン１１の駆動力の伝達を遮断可能な位置に配置されたクラッチ装置２と、リヤディファレンシャル１６と左後輪１４Ｌとの間に配置されたトルクカップリング３とを有している。クラッチ装置２は、フロントディファレンシャル１５と共にトランスファケース１００に収容されている。   The driving force transmission system 10 is disposed together with the front differential 15 and the rear differential 16 on a driving force transmission path from the transmission 12 to the front wheels 13L and 13R and the rear wheels 14L and 14R in the four-wheel drive vehicle 1. The driving force transmission system 10 includes a propeller shaft 17 that transmits the driving force (torque) of the engine 11 from the front wheels 13L and 13R to the rear wheels 14L and 14R, and the upstream side of the driving force transmission path from the propeller shaft 17. The clutch device 2 is disposed at a position where the transmission of the driving force of the engine 11 can be cut off, and the torque coupling 3 is disposed between the rear differential 16 and the left rear wheel 14L. The clutch device 2 is accommodated in the transfer case 100 together with the front differential 15.

クラッチ装置２及びトルクカップリング３は、制御装置４によって制御される。制御装置４には、プロペラシャフト１７の回転数を検出する第１回転センサ４１、及びフロントディファレンシャル１５のフロントデフケース１５０の回転数を検出する第２回転センサ４２が接続されている。   The clutch device 2 and the torque coupling 3 are controlled by the control device 4. A first rotation sensor 41 that detects the rotation speed of the propeller shaft 17 and a second rotation sensor 42 that detects the rotation speed of the front differential case 150 of the front differential 15 are connected to the control device 4.

前輪１３Ｌ，１３Ｒには、エンジン１１の駆動力がトランスミッション１２及びフロントディファレンシャル１５を介して常に伝達される。後輪１４Ｌ，１４Ｒには、エンジン１１の駆動力がトランスミッション１２、クラッチ装置２、プロペラシャフト１７、トルクカップリング３、及びリヤディファレンシャル１６を介して伝達される。制御装置４は、例えば前輪１３Ｌ，１３Ｒと後輪１４Ｌ，１４Ｒとの差動回転数や運転者によるアクセルペダルによる加速操作量等の走行状態に基づいて、クラッチ装置２及びトルクカップリング３を制御する。   The driving force of the engine 11 is always transmitted to the front wheels 13L and 13R via the transmission 12 and the front differential 15. The driving force of the engine 11 is transmitted to the rear wheels 14L and 14R via the transmission 12, the clutch device 2, the propeller shaft 17, the torque coupling 3, and the rear differential 16. The control device 4 controls the clutch device 2 and the torque coupling 3 based on, for example, a driving state such as a differential rotation speed between the front wheels 13L and 13R and the rear wheels 14L and 14R and an acceleration operation amount by an accelerator pedal by a driver. To do.

フロントディファレンシャル１５は、左右のサイドギヤ１５１Ｌ，１５１Ｒ、一対のピニオンギヤ１５２、一対のピニオンギヤ１５２を回転可能に軸支するピニオンシャフト１５３、及びピニオンシャフト１５３を支持するフロントデフケース１５０を有している。フロントデフケース１５０には、トランスミッション１２から出力される駆動力が歯車の噛み合いによって直接的に伝達される。   The front differential 15 includes left and right side gears 151L and 151R, a pair of pinion gears 152, a pinion shaft 153 that rotatably supports the pair of pinion gears 152, and a front differential case 150 that supports the pinion shaft 153. The driving force output from the transmission 12 is directly transmitted to the front differential case 150 by the meshing of the gears.

サイドギヤ１５１Ｌは、前輪側のアクスルシャフト１５４Ｌを介して左前輪１３Ｌに連結されている。サイドギヤ１５１Ｒは、前輪側のアクスルシャフト１５４Ｒを介して右前輪１３Ｒに連結されている。一対のピニオンギヤ１５２は、サイドギヤ１５１Ｌ，１５１Ｒにギヤ軸を直交させて噛み合っている。また、フロントデフケース１５０には、アクスルシャフト１５４Ｒに沿って延びる筒部１５０ａが形成されている。   The side gear 151L is connected to the left front wheel 13L via a front wheel side axle shaft 154L. The side gear 151R is coupled to the right front wheel 13R via a front wheel side axle shaft 154R. The pair of pinion gears 152 mesh with the side gears 151L and 151R with their gear axes orthogonal to each other. Further, the front differential case 150 is formed with a cylindrical portion 150a extending along the axle shaft 154R.

リヤディファレンシャル１６は、左右のサイドギヤ１６１Ｌ，１６１Ｒ、一対のピニオンギヤ１６２、一対のピニオンギヤ１６２を回転可能に軸支するピニオンシャフト１６３、及びピニオンシャフト１６３を支持するリヤデフケース１６０を有している。サイドギヤ１６１Ｌは、トルクカップリング３及び後輪側のアクスルシャフト１６３Ｌを介して左後輪１４Ｌに連結されている。サイドギヤ１６１Ｒは、後輪側のアクスルシャフト１６３Ｒを介して右後輪１４Ｒに連結されている。   The rear differential 16 includes left and right side gears 161L and 161R, a pair of pinion gears 162, a pinion shaft 163 that rotatably supports the pair of pinion gears 162, and a rear differential case 160 that supports the pinion shaft 163. The side gear 161L is connected to the left rear wheel 14L via the torque coupling 3 and the axle shaft 163L on the rear wheel side. The side gear 161R is connected to the right rear wheel 14R via a rear wheel axle shaft 163R.

プロペラシャフト１７の前輪側端部には、互いに噛み合うドライブピニオン１８１及びリングギヤ１８２からなる前輪側のかさ歯車機構１８が配置されている。ドライブピニオン１８１は、プロペラシャフト１７と一体に回転する。リングギヤ１８２は、クラッチ装置２を介してエンジン１１の駆動力を受ける。   A front wheel side bevel gear mechanism 18 including a drive pinion 181 and a ring gear 182 that are meshed with each other is disposed at the front wheel side end of the propeller shaft 17. The drive pinion 181 rotates integrally with the propeller shaft 17. Ring gear 182 receives the driving force of engine 11 through clutch device 2.

プロペラシャフト１７の後輪側端部には、互いに噛み合うピニオンギヤ１９１及びリングギヤ１９２からなる後輪側のかさ歯車機構１９が配置されている。ピニオンギヤ１９１は、プロペラシャフト１７と一体に回転する。リングギヤ１９２はリヤディファレンシャル１６のリヤデフケース１６０と一体に回転する。   A rear wheel side bevel gear mechanism 19 including a pinion gear 191 and a ring gear 192 that mesh with each other is disposed at the rear wheel side end of the propeller shaft 17. The pinion gear 191 rotates integrally with the propeller shaft 17. The ring gear 192 rotates integrally with the rear differential case 160 of the rear differential 16.

トルクカップリング３は、リヤディファレンシャル１６のサイドギヤ１６１Ｌに相対回転不能に連結された有底円筒状のハウジング３０と、アクスルシャフト１６３Ｌに相対回転不能に連結された軸状のインナシャフト３１と、ハウジング３０とインナシャフト３１との間に配置された多板クラッチ３２と、制御装置４から電流が供給される電磁コイル３３と、電磁コイル３３の磁力によって作動し、ハウジング３０とインナシャフト３１との相対回転に基づいて多板クラッチ３２を押圧するカム機構３４とを有している。トルクカップリング３は、カム機構３４が電磁コイル３３の通電量に応じたカム推力で多板クラッチ３２を押圧し、ハウジング３０とインナシャフト３１との間で駆動力を伝達する。   The torque coupling 3 includes a bottomed cylindrical housing 30 connected to the side gear 161L of the rear differential 16 so as not to rotate relative thereto, an axial inner shaft 31 connected to the axle shaft 163L so as not to rotate relative thereto, and a housing 30. And the inner shaft 31, a multi-plate clutch 32, an electromagnetic coil 33 to which electric current is supplied from the control device 4, and a magnetic force of the electromagnetic coil 33, and the relative rotation between the housing 30 and the inner shaft 31. And a cam mechanism 34 that presses the multi-plate clutch 32. In the torque coupling 3, the cam mechanism 34 presses the multi-plate clutch 32 with a cam thrust according to the energization amount of the electromagnetic coil 33, and transmits a driving force between the housing 30 and the inner shaft 31.

四輪駆動車１が４輪駆動状態で走行する際には、制御装置４による制御によってクラッチ装置２及びトルクカップリング３が共に駆動力を伝達可能な作動状態となり、エンジン１１の駆動力がクラッチ装置２を介してフロントデフケース１５０からプロペラシャフト１７に伝達され、さらにプロペラシャフト１７からリヤディファレンシャル１６に伝達される。リヤディファレンシャル１６に伝達された駆動力は、サイドギヤ１６１Ｌからトルクカップリング３及びアクスルシャフト１６３Ｌを介して左後輪１４Ｌに配分されると共に、サイドギヤ１６１Ｒからアクスルシャフト１６３Ｒを介して右後輪１４Ｒに配分される。トルクカップリング３を介してアクスルシャフト１６３Ｌに伝達される駆動力は、制御装置４から電磁コイル３３に供給される電流量に応じて変化する。また、アクスルシャフト１６３Ｒにも、アクスルシャフト１６３Ｌに伝達される駆動力に対応する駆動力が伝達される。   When the four-wheel drive vehicle 1 travels in a four-wheel drive state, the clutch device 2 and the torque coupling 3 are both in an operating state in which the drive force can be transmitted by the control of the control device 4, and the drive force of the engine 11 is It is transmitted from the front differential case 150 to the propeller shaft 17 via the device 2 and further transmitted from the propeller shaft 17 to the rear differential 16. The driving force transmitted to the rear differential 16 is distributed from the side gear 161L to the left rear wheel 14L via the torque coupling 3 and the axle shaft 163L, and from the side gear 161R to the right rear wheel 14R via the axle shaft 163R. Is done. The driving force transmitted to the axle shaft 163L via the torque coupling 3 changes according to the amount of current supplied from the control device 4 to the electromagnetic coil 33. A driving force corresponding to the driving force transmitted to the axle shaft 163L is also transmitted to the axle shaft 163R.

一方、前輪１３Ｌ，１３Ｒのみに駆動力が伝達される２輪駆動状態で走行する際には、クラッチ装置２及びトルクカップリング３が共に駆動力の伝達を遮断する非作動状態となる。この際、走行に伴って後輪１４Ｒと共にリヤディファレンシャル１６のサイドギヤ１６１Ｒが回転するが、アクスルシャフト１６３Ｌとサイドギヤ１６１Ｌとの連結はトルクカップリング３により遮断されているので、一対のピニオンギヤ１６２が空転し、リヤデフケース１６０は回転しない。つまり、２輪駆動状態での走行時には、プロペラシャフト１７の回転が停止する。これにより、プロペラシャフト１７や前輪側のかさ歯車機構１８及び後輪側のかさ歯車機構１９の各部の回転に伴う回転抵抗が抑制され、走行抵抗が低減されることから、２輪駆動状態における四輪駆動車１の燃費が改善される。   On the other hand, when the vehicle travels in a two-wheel drive state in which the driving force is transmitted only to the front wheels 13L and 13R, both the clutch device 2 and the torque coupling 3 are in an inoperative state in which the transmission of the driving force is interrupted. At this time, the side gear 161R of the rear differential 16 rotates together with the rear wheel 14R as the vehicle travels. However, since the connection between the axle shaft 163L and the side gear 161L is interrupted by the torque coupling 3, the pair of pinion gears 162 idle. The rear differential case 160 does not rotate. That is, during traveling in the two-wheel drive state, the rotation of the propeller shaft 17 is stopped. As a result, the rotational resistance associated with the rotation of each part of the propeller shaft 17, the front wheel side bevel gear mechanism 18 and the rear wheel side bevel gear mechanism 19 is suppressed, and the running resistance is reduced. The fuel efficiency of the wheel drive vehicle 1 is improved.

また、制御装置４は、四輪駆動車１を２輪駆動状態から４輪駆動状態に移行させる際、まずトルクカップリング３を作動させてプロペラシャフト１７を回転させ、第１回転センサ４１及び第２回転センサ４２の検出値に基づいてクラッチ装置２における回転が同期したと判定したとき、クラッチ装置２を作動させる。以下、クラッチ装置２及びその周辺部の構成について、より詳細に説明する。   Further, when the control device 4 shifts the four-wheel drive vehicle 1 from the two-wheel drive state to the four-wheel drive state, the control device 4 first operates the torque coupling 3 to rotate the propeller shaft 17, and the first rotation sensor 41 and the first rotation sensor 41. When it is determined that the rotation of the clutch device 2 is synchronized based on the detection value of the two-rotation sensor 42, the clutch device 2 is operated. Hereinafter, the configuration of the clutch device 2 and its peripheral part will be described in more detail.

（クラッチ装置の構成）
図２は、クラッチ装置２及びその周辺部の構成例を示す断面図である。図３は、図２におけるクラッチ装置２の要部拡大図である。 (Configuration of clutch device)
FIG. 2 is a cross-sectional view showing a configuration example of the clutch device 2 and its peripheral portion. FIG. 3 is an enlarged view of a main part of the clutch device 2 in FIG.

トランスファケース１００は、第１ケース部材１０１及び第２ケース部材１０２を有している。第１ケース部材１０１及び第２ケース部材１０２は、図略のボルトによって相互に固定されている。クラッチ装置２は、第１ケース部材１０１及び第２ケース部材１０２にわたって収容されている。また、第２ケース部材１０２は、アクスルシャフト１５４Ｒを導出する導出口を有し、この導出口の内面とアクスルシャフト１５４Ｒとの間がシール部材２９０によってシールされている。   The transfer case 100 includes a first case member 101 and a second case member 102. The first case member 101 and the second case member 102 are fixed to each other by unillustrated bolts. The clutch device 2 is accommodated over the first case member 101 and the second case member 102. Further, the second case member 102 has a lead-out port that leads out the axle shaft 154R, and the inner surface of the lead-out port and the axle shaft 154R are sealed by a seal member 290.

クラッチ装置２は、前輪側のかさ歯車機構１８のリングギヤ１８２と、フロントデフケース１５０の筒部１５０ａに相対回転不能に連結された円筒状の入力軸部材２０とを係脱可能に連結する。ここで、係脱可能とは、後述する連結部材２１が入力軸部材２０及びリングギヤ１８２に共に係合し、入力軸部材２０とリングギヤ１８２とが駆動力伝達可能に連結された連結状態と、連結部材２１の移動によってこの連結状態を脱し、入力軸部材２０とリングギヤ１８２とが相対回転可能な非連結状態とを切り替え可能であることをいう。入力軸部材２０は、本発明の第１部材の一態様であり、リングギヤ１８２は、本発明の第２部材の一態様である。   The clutch device 2 removably connects the ring gear 182 of the bevel gear mechanism 18 on the front wheel side and the cylindrical input shaft member 20 that is connected to the cylindrical portion 150a of the front differential case 150 so as not to be relatively rotatable. Here, “engageable / disengageable” means that the connecting member 21 described later is engaged with the input shaft member 20 and the ring gear 182 together, and the input shaft member 20 and the ring gear 182 are connected so as to be able to transmit the driving force. This means that the connected state can be released by the movement of the member 21 and the input shaft member 20 and the ring gear 182 can be switched to a non-connected state in which the relative rotation is possible. The input shaft member 20 is an aspect of the first member of the present invention, and the ring gear 182 is an aspect of the second member of the present invention.

クラッチ装置２は、入力軸部材２０及びリングギヤ１８２に係合して入力軸部材２０とリングギヤ１８２とを連結する連結位置、及び入力軸部材２０とリングギヤ１８２とを相対回転可能とする非連結位置の間を軸方向に進退移動する環状の連結部材２１と、連結部材２１を軸方向に沿って弾性的に付勢する弾性部材２２と、連結部材２１を弾性部材２２の付勢力に抗して軸方向に押圧する押圧部材２３と、押圧部材２３を連結部材２１に対して相対回転させる回転力を付与する回転力付与機構２ａとを有している。   The clutch device 2 is engaged at the input shaft member 20 and the ring gear 182 to connect the input shaft member 20 and the ring gear 182 and at a non-connecting position where the input shaft member 20 and the ring gear 182 can be rotated relative to each other. An annular connecting member 21 that moves forward and backward in the axial direction, an elastic member 22 that elastically biases the connecting member 21 along the axial direction, and a shaft that resists the biasing force of the elastic member 22. A pressing member 23 that presses in the direction and a rotational force applying mechanism 2 a that applies a rotational force that rotates the pressing member 23 relative to the connecting member 21 are provided.

回転力付与機構２ａは、通電により磁力を発生する電磁コイル２４と、電磁コイル２４を支持するヨーク２５と、電磁コイル２４の磁力によってヨーク２５に引き寄せられるアーマチャ２６とを有する電磁ブレーキ機構である。この回転力付与機構２ａは、電磁コイル２４への通電によって作動し、アーマチャ２６がヨーク２５に引き寄せられることによってアーマチャ２６とヨーク２５とが当接し、アーマチャ２６とヨーク２５との当接面に発生する摩擦力を押圧部材２３に付与することで、押圧部材２３を連結部材２１に対して相対回転させる。   The rotational force imparting mechanism 2 a is an electromagnetic brake mechanism having an electromagnetic coil 24 that generates a magnetic force when energized, a yoke 25 that supports the electromagnetic coil 24, and an armature 26 that is attracted to the yoke 25 by the magnetic force of the electromagnetic coil 24. The rotational force applying mechanism 2 a is activated by energizing the electromagnetic coil 24, and the armature 26 and the yoke 25 come into contact with each other when the armature 26 is attracted to the yoke 25, and is generated on the contact surface between the armature 26 and the yoke 25. By applying a friction force to the pressing member 23, the pressing member 23 is rotated relative to the connecting member 21.

また、連結部材２１及び押圧部材２３のそれぞれの一部は、連結部材２１及び押圧部材２３のうち、一方の部材に設けられたカム部と他方の部材に設けられた突起とからなるカム機構を構成する。カム部と突起とは、弾性部材２２の付勢力によって当接する。本実施の形態では、連結部材２１にカム部２１０が設けられ、押圧部材２３に突起２３１が設けられている。このカム機構により、連結部材２１が押圧部材２３に対して軸方向に移動する。   In addition, each of the connecting member 21 and the pressing member 23 includes a cam mechanism including a cam portion provided on one member and a protrusion provided on the other member of the connecting member 21 and the pressing member 23. Configure. The cam portion and the protrusion are brought into contact with each other by the urging force of the elastic member 22. In the present embodiment, the connecting member 21 is provided with a cam portion 210, and the pressing member 23 is provided with a protrusion 231. By this cam mechanism, the connecting member 21 moves in the axial direction with respect to the pressing member 23.

入力軸部材２０は、前輪側のアクスルシャフト１５４Ｒを内部に挿通させる円筒状であり、その回転軸線Ｏ方向に沿った軸方向の一端部がフロントデフケース１５０の筒部１５０ａにスプライン係合している。これにより、入力軸部材２０はフロントデフケース１５０に相対回転不能に連結されている。また、入力軸部材２０は、フロントデフケース１５０側の一端部が第１の玉軸受２９１によってトランスファケース１００の第１ケース部材１０１に回転可能に支持され、他端部が第２の玉軸受２９２によってトランスファケース１００の第２ケース部材１０２に回転可能に支持されている。入力軸部材２０の軸方向の一部における外周面には、連結部材２１とスプライン係合するスプライン係合部２０１が外方に突出して形成されている。   The input shaft member 20 has a cylindrical shape through which the axle shaft 154R on the front wheel side is inserted, and one end portion in the axial direction along the direction of the rotation axis O is spline-engaged with the cylindrical portion 150a of the front differential case 150. . Thereby, the input shaft member 20 is connected to the front differential case 150 so as not to be relatively rotatable. The input shaft member 20 is rotatably supported at one end on the front differential case 150 side by a first ball bearing 291 on the first case member 101 of the transfer case 100 and at the other end by a second ball bearing 292. The transfer case 100 is rotatably supported by the second case member 102. A spline engaging portion 201 that splines engages with the connecting member 21 is formed on the outer peripheral surface of a part of the input shaft member 20 in the axial direction so as to protrude outward.

入力軸部材２０の外周側には、円筒状のプランジャ２７及びスペーサ２８１が配置されている。プランジャ２７は、入力軸部材２０のスプライン係合部２０１よりもフロントデフケース１５０側に、スペーサ２８１はその反対側に、それぞれ配置されている。プランジャ２７は、円筒部２７０と、円筒部２７０におけるフロントデフケース１５０側の一端部に外方に張り出して形成されたフランジ部２７１とを一体に有している。   A cylindrical plunger 27 and a spacer 281 are disposed on the outer peripheral side of the input shaft member 20. The plunger 27 is disposed on the front differential case 150 side of the spline engaging portion 201 of the input shaft member 20, and the spacer 281 is disposed on the opposite side thereof. The plunger 27 integrally includes a cylindrical portion 270 and a flange portion 271 formed to project outward from one end portion of the cylindrical portion 270 on the front differential case 150 side.

プランジャ２７のフランジ部２７１とトランスファケース１００の第１ケース部材１０１に形成された内方突起１０１ａとの間には、弾性部材２２が軸方向に圧縮された状態で配置されている。本実施の形態では、弾性部材２２がコイルバネからなる。ただし、弾性部材２２は、例えば複数の皿バネを軸方向に配列して構成してもよく、ゴム等の弾性体によって構成してもよい。   Between the flange portion 271 of the plunger 27 and the inward projection 101a formed on the first case member 101 of the transfer case 100, the elastic member 22 is disposed in a state compressed in the axial direction. In the present embodiment, the elastic member 22 is a coil spring. However, the elastic member 22 may be configured by, for example, arranging a plurality of disc springs in the axial direction, or may be configured by an elastic body such as rubber.

プランジャ２７のフランジ部２７１と弾性部材２２との間には、プランジャ２７の回転を円滑にするための針状スラストころ軸受２９３が配置されている。弾性部材２２は、針状スラストころ軸受２９３及びプランジャ２７を介して連結部材２１を入力軸部材２０のスプライン係合部２０１側に押し付けている。また、連結部材２１がスプライン係合部２０１に係合すると、プランジャ２７における円筒部２７０の他端部（弾性部材２２側とは反対側の端部）がスプライン係合部２０１に突き当たる。   Between the flange portion 271 of the plunger 27 and the elastic member 22, a needle thrust roller bearing 293 for facilitating the rotation of the plunger 27 is disposed. The elastic member 22 presses the connecting member 21 against the spline engaging portion 201 side of the input shaft member 20 via the needle-like thrust roller bearing 293 and the plunger 27. Further, when the connecting member 21 is engaged with the spline engaging portion 201, the other end portion of the cylindrical portion 270 of the plunger 27 (an end portion opposite to the elastic member 22 side) abuts against the spline engaging portion 201.

プランジャ２７における円筒部２７０の外側には、リングギヤ１８２に相対回転不能に結合され、リングギヤ１８２を支持する環状支持部材２８２が配置されている。環状支持部材２８２は、第１の円錐ころ軸受２９４を介してトランスファケース１００の第１ケース部材１０１に回転可能に支持されている。この環状支持部材２８２には、連結部材２１の軸方向端面２１ａが対向している。また、リングギヤ１８２は、第２の円錐ころ軸受２９５を介して、トランスファケース１００の第２ケース部材１０２にも支持されている。   An annular support member 282 that is coupled to the ring gear 182 so as not to be relatively rotatable and supports the ring gear 182 is disposed outside the cylindrical portion 270 of the plunger 27. The annular support member 282 is rotatably supported by the first case member 101 of the transfer case 100 via the first tapered roller bearing 294. The annular support member 282 is opposed to the axial end surface 21 a of the connecting member 21. The ring gear 182 is also supported by the second case member 102 of the transfer case 100 via the second tapered roller bearing 295.

リングギヤ１８２の内周面には、連結部材２１とスプライン係合するスプライン係合部１８３が形成されている。このスプライン係合部１８３は、その一部が入力軸部材２０のスプライン係合部２０１に対向し、入力軸部材２０のスプライン係合部２０１よりも軸方向に長い範囲に形成されている。   A spline engaging portion 183 that is spline engaged with the connecting member 21 is formed on the inner peripheral surface of the ring gear 182. A part of the spline engaging portion 183 faces the spline engaging portion 201 of the input shaft member 20 and is formed in a range longer than the spline engaging portion 201 of the input shaft member 20 in the axial direction.

ヨーク２５は、鉄系金属からなる磁性体であり、トランスファケース１００の第２ケース部材１０２の内面に嵌着されている。ヨーク２５には、電磁コイル２４を収容する環状の凹部２５ａが形成されている。また、ヨーク２５は、入力軸部材２０に向かって内方に張り出して形成された張出部２５１を有し、この張出部２５１と押圧部材２３との間に針状スラストころ軸受２９６が配置されている。押圧部材２３は、ヨーク２５の張出部２５１によって連結部材２１から離間する方向の軸方向移動が規制されると共に、針状スラストころ軸受２９６によってヨーク２５に対して円滑に回転可能である。   The yoke 25 is a magnetic body made of iron-based metal, and is fitted on the inner surface of the second case member 102 of the transfer case 100. The yoke 25 is formed with an annular recess 25 a for accommodating the electromagnetic coil 24. Further, the yoke 25 has an overhang portion 251 formed to protrude inward toward the input shaft member 20, and a needle thrust roller bearing 296 is disposed between the overhang portion 251 and the pressing member 23. Has been. The pressing member 23 is restricted from axial movement in a direction away from the connecting member 21 by the overhanging portion 251 of the yoke 25, and can be smoothly rotated with respect to the yoke 25 by the needle-like thrust roller bearing 296.

図３に示すように、押圧部材２３は、円筒状のスペーサ２８１の外周側に配置され、環状の基部２３０と、基部２３０から連結部材２１側に向かって突出した複数の突起２３１とを有している。基部２３０には、穴部２３０ａが周方向の複数箇所（本実施の形態では３箇所）に等間隔に形成されている。突起２３１は、円柱状であり、その先端部２３１ａは半球状である。突起２３１の基端部２３１ｂは、例えば穴部２３０ａへの圧入によって基部２３０に固定されている。なお、本実施の形態では、押圧部材２３が、基部２３０と複数の突起２３１との組み合わせによって構成されているが、これらを一体の部材として構成してもよい。   As shown in FIG. 3, the pressing member 23 is disposed on the outer peripheral side of the cylindrical spacer 281, and has an annular base portion 230 and a plurality of protrusions 231 that protrude from the base portion 230 toward the connecting member 21 side. ing. In the base 230, holes 230a are formed at a plurality of locations in the circumferential direction (three locations in the present embodiment) at equal intervals. The protrusion 231 has a cylindrical shape, and the tip 231a has a hemispherical shape. The base end portion 231b of the protrusion 231 is fixed to the base portion 230, for example, by press fitting into the hole portion 230a. In addition, in this Embodiment, although the pressing member 23 is comprised by the combination of the base 230 and the some protrusion 231, you may comprise these as an integral member.

アーマチャ２６は、鉄系金属からなる環板状の磁性体であり、制御装置４から電磁コイル２４へ供給される電流によって発生する磁力によって、ヨーク２５に引き寄せられる。制御装置４は、電磁コイル２４へ供給する電流の電流値を複数段階に調節することが可能である。押圧部材２３は、アーマチャ２６と軸方向に相対移動可能かつ相対回転不能に係合している。より具体的には、アーマチャ２６には、軸方向に貫通して形成された挿通孔２６ａが複数箇所（本実施の形態では３箇所）に設けられ、押圧部材２３の突起２３１がこの挿通孔２６ａを挿通している。この構成により、アーマチャ２６は、突起２３１に案内されて回転軸線Ｏに沿って移動可能である。   The armature 26 is an annular plate-shaped magnetic body made of an iron-based metal, and is attracted to the yoke 25 by a magnetic force generated by a current supplied from the control device 4 to the electromagnetic coil 24. The control device 4 can adjust the current value of the current supplied to the electromagnetic coil 24 in a plurality of stages. The pressing member 23 is engaged with the armature 26 so as to be relatively movable in the axial direction and not to be relatively rotatable. More specifically, the armature 26 is provided with insertion holes 26a that are formed so as to penetrate in the axial direction at a plurality of locations (three locations in the present embodiment), and the protrusions 231 of the pressing member 23 are formed in the insertion holes 26a. Is inserted. With this configuration, the armature 26 can be moved along the rotation axis O while being guided by the protrusion 231.

電磁コイル２４へ通電されると、アーマチャ２６の一方の側面がヨーク２５の端面２５ｂに当接し、ヨーク２５との間に摩擦力が発生する。この摩擦力は、挿通孔２６ａを挿通する突起２３１において押圧部材２３に付与される。つまり、押圧部材２３は、複数の突起２３１がアーマチャ２６の複数の挿通孔２６ａをそれぞれ挿通することで、電磁コイル２４への通電時において、アーマチャ２６とヨーク２５との間に発生する摩擦力を受ける。押圧部材２３は、この摩擦力によって連結部材２１に対して相対回転する。   When the electromagnetic coil 24 is energized, one side surface of the armature 26 comes into contact with the end surface 25 b of the yoke 25, and a frictional force is generated between the armature 26 and the yoke 25. This frictional force is applied to the pressing member 23 at the protrusion 231 inserted through the insertion hole 26a. In other words, the pressing member 23 causes the plurality of protrusions 231 to pass through the plurality of insertion holes 26 a of the armature 26, respectively, so that a frictional force generated between the armature 26 and the yoke 25 is generated when the electromagnetic coil 24 is energized. receive. The pressing member 23 rotates relative to the connecting member 21 by this frictional force.

つまり、四輪駆動車１の走行時において、連結部材２１はリングギヤ１８２と共に回転するので、トランスファケース１００に嵌着されたヨーク２５とアーマチャ２６との間に発生する摩擦力が押圧部材２３に付与されると、押圧部材２３と連結部材２１とが相対的に回転する。すなわち、回転力付与機構２ａは、リングギヤ１８２の回転に応じて回転する連結部材２１と押圧部材２３とを、アーマチャ２６とヨーク２５との間に発生する摩擦力によってアーマチャ２６の回転を抑制することで相対回転させる。   That is, when the four-wheel drive vehicle 1 is traveling, the connecting member 21 rotates together with the ring gear 182, so that a frictional force generated between the yoke 25 fitted to the transfer case 100 and the armature 26 is applied to the pressing member 23. If it does, the press member 23 and the connection member 21 will rotate relatively. That is, the rotational force applying mechanism 2 a suppresses the rotation of the armature 26 by the frictional force generated between the armature 26 and the yoke 25, and the connecting member 21 and the pressing member 23 that rotate according to the rotation of the ring gear 182. Rotate relative with.

図３に示すように、連結部材２１は、入力軸部材２０とスプライン係合する第１スプライン係合部２１１を内周面に有し、かつリングギヤ１８２とスプライン係合する第２スプライン係合部２１２を外周面に有している。第１スプライン係合部２１１及び第２スプライン係合部２１２は、回転軸線Ｏに平行な軸方向に延びる複数のスプライン歯からなる。   As shown in FIG. 3, the connecting member 21 has a first spline engaging portion 211 that is spline engaged with the input shaft member 20 on the inner peripheral surface, and a second spline engaging portion that is spline engaged with the ring gear 182. 212 is provided on the outer peripheral surface. The first spline engaging portion 211 and the second spline engaging portion 212 are composed of a plurality of spline teeth extending in the axial direction parallel to the rotation axis O.

連結部材２１は、入力軸部材２０とリングギヤ１８２とを連結する連結位置にあるとき、第１スプライン係合部２１１が入力軸部材２０のスプライン係合部２０１にスプライン係合すると共に、第２スプライン係合部２１２がリングギヤ１８２のスプライン係合部１８３にスプライン係合する。また、連結部材２１は、入力軸部材２０とリングギヤ１８２とを相対回転可能とする非連結位置にあるとき、第２スプライン係合部２１２がリングギヤ１８２のスプライン係合部１８３にスプライン係合するが、第１スプライン係合部２１１は入力軸部材２０のスプライン係合部２０１にスプライン係合しない。つまり、連結部材２１は、リングギヤ１８２と連結位置及び非連結位置において係合し、入力軸部材２０とは連結位置においてのみ係合する。図２では、回転軸線Ｏよりも上側に連結部材２１が連結位置にある状態を示し、回転軸線Ｏよりも下側に連結部材２１が連結位置にある状態を示している。   When the connecting member 21 is in a connecting position for connecting the input shaft member 20 and the ring gear 182, the first spline engaging portion 211 is spline engaged with the spline engaging portion 201 of the input shaft member 20, and the second spline is connected. The engaging portion 212 is spline engaged with the spline engaging portion 183 of the ring gear 182. Further, when the connecting member 21 is in a non-connecting position where the input shaft member 20 and the ring gear 182 can be rotated relative to each other, the second spline engaging portion 212 is spline engaged with the spline engaging portion 183 of the ring gear 182. The first spline engaging portion 211 is not spline engaged with the spline engaging portion 201 of the input shaft member 20. That is, the connecting member 21 engages with the ring gear 182 at the connecting position and the non-connecting position, and engages with the input shaft member 20 only at the connecting position. FIG. 2 shows a state in which the connecting member 21 is in the connecting position above the rotation axis O, and shows a state in which the connecting member 21 is in the connecting position below the rotation axis O.

連結部材２１には、第１スプライン係合部２１１と第２スプライン係合部２１２との間の径方向の中央部に、カム部２１０が形成されている。また、連結部材２１には、カム部２１０の内周側に内鍔部２１３が形成され、カム部２１０の外周側に外鍔部２１４が形成されている。内鍔部２１３及び外鍔部２１４は、押圧部材２３側に突出し、内鍔部２１３と外鍔部２１４との間から押圧部材２３の突起２３１がカム部２１０に当接する。次に、このカム部２１０の構成について詳細に説明する。   In the connecting member 21, a cam portion 210 is formed at a central portion in the radial direction between the first spline engaging portion 211 and the second spline engaging portion 212. Further, the connecting member 21 has an inner flange portion 213 formed on the inner peripheral side of the cam portion 210, and an outer flange portion 214 formed on the outer peripheral side of the cam portion 210. The inner flange portion 213 and the outer flange portion 214 protrude toward the pressing member 23, and the protrusion 231 of the pressing member 23 contacts the cam portion 210 from between the inner flange portion 213 and the outer flange portion 214. Next, the configuration of the cam portion 210 will be described in detail.

図４は、カム部２１０の構成を模式的に説明する説明図である。図４（ａ）は、環状のカム部２１０を平面上に展開し、連結部材２１の径方向にあたる方向から見た状態を示している。図４（ｂ）は、図４（ａ）のＢ部拡大図である。   FIG. 4 is an explanatory diagram schematically illustrating the configuration of the cam unit 210. FIG. 4A shows a state in which the annular cam portion 210 is developed on a plane and viewed from a direction corresponding to the radial direction of the connecting member 21. FIG.4 (b) is the B section enlarged view of Fig.4 (a).

カム部２１０は、連結部材２１が非連結位置にあるときに突起２３１の先端部２３１ａが当接する第１凹部２１０ａと、第１凹部２１０ａに対して軸方向にずれた位置に形成され、連結部材２１が連結位置にあるときに突起２３１の先端部２３１ａが当接する第２凹部２１０ｂとを有している。本実施の形態では、第１凹部２１０ａ及び第２凹部２１０ｂが周方向の３箇所にそれぞれ形成されている。第１凹部２１０ａ及び第２凹部２１０ｂは、その底部２１０ａ１，２１０ｂ１が軸方向端面２１ａに向かうように、軸方向に窪んでいる。 The cam portion 210 is formed at a position where the tip portion 231a of the protrusion 231 contacts when the connecting member 21 is in the non-connecting position, and a position offset in the axial direction with respect to the first recess 210a. And a second recess 210b with which the tip 231a of the projection 231 comes into contact when 21 is in the coupling position. In the present embodiment, the first recess 210a and the second recess 210b are respectively formed at three locations in the circumferential direction. The first concave portion 210a and the second concave portion 210b are recessed in the axial direction so that the bottom portions 210a 1 and 210b 1 face the axial end surface 21a.

第１凹部２１０ａと第２凹部２１０ｂとの間には、回転軸線Ｏに対して直交する面（仮想面）に対して傾斜した第１乃至第３カム面２１０ｃ，２１０ｄ，２１０ｅが形成されている。連結部材２１は、回転力付与機構２ａの作動によって連結部材２１と押圧部材２３とが相対回転し、突起２３１の先端部２３１ａが第１凹部２１０ａと第２凹部２１０ｂとの間に形成された第１乃至第３カム面２１０ｃ，２１０ｄ，２１０ｅを摺動することで、連結位置と非連結位置との間を進退移動する。   Between the 1st recessed part 210a and the 2nd recessed part 210b, the 1st thru | or 3rd cam surface 210c, 210d, 210e inclined with respect to the surface (virtual surface) orthogonal to the rotating shaft O is formed. . In the connecting member 21, the connecting member 21 and the pressing member 23 are rotated relative to each other by the operation of the rotational force applying mechanism 2a, and the tip portion 231a of the protrusion 231 is formed between the first recess 210a and the second recess 210b. By sliding on the first to third cam surfaces 210c, 210d, and 210e, it moves forward and backward between the connected position and the non-connected position.

第１凹部２１０ａは、第２凹部２１０ｂよりも押圧部材２３側（基部２３０側）に位置している。これにより、カム部２１０の軸方向の厚みは、第１凹部２１０ａにおいて第２凹部２１０ｂよりも厚く形成されている。第１凹部２１０ａの底部２１０ａ１と第２凹部２１０ｂの底部２１０ｂ１との間の軸方向の距離をｄ１とすると、連結部材２１は、押圧部材２３との相対回転により、この距離ｄ１の範囲で往復運動する。 The first recess 210a is located closer to the pressing member 23 (base 230 side) than the second recess 210b. Thereby, the axial thickness of the cam portion 210 is formed thicker in the first recess 210a than in the second recess 210b. When the bottom 210a 1 of the first recess 210a to the axial distance between the bottom 210b 1 of the second recess 210b to d 1, connecting member 21, the relative rotation of the pressing member 23, the distance d 1 Reciprocate in range.

なお、図４（ａ）の中央部及び図４（ｂ）では、説明のために第１凹部２１０ａ及び第２凹部２１０ｂに当接した突起２３１をそれぞれ仮想線（二点鎖線）で示しているが、実際には、複数の突起２３１のうち１つの突起２３１が第１凹部２１０ａに当接する際には他の突起２３１も同時に第１凹部２１０ａに当接し、複数の突起２３１のうち１つの突起２３１が第２凹部２１０ｂに当接する際には他の突起２３１も同時に第２凹部２１０ｂに当接する。また、四輪駆動車１の前進時において、連結部材２１に対する押圧部材２３の相対的な移動方向は、図４（ａ）に示す矢印Ａ方向である。   4A and 4B, the protrusions 231 that are in contact with the first concave portion 210a and the second concave portion 210b are indicated by phantom lines (two-dot chain lines) for the sake of explanation. However, actually, when one projection 231 of the plurality of projections 231 contacts the first recess 210a, the other projection 231 also contacts the first recess 210a at the same time. When 231 contacts the second recess 210b, the other protrusions 231 also contact the second recess 210b at the same time. Further, when the four-wheel drive vehicle 1 moves forward, the relative movement direction of the pressing member 23 with respect to the connecting member 21 is an arrow A direction shown in FIG.

カム部２１０は、第１凹部２１０ａの底部２１０ａ１から連結部材２１の周方向に矢印Ａ方向（押圧部材２３の相対回転方向）に向かって延びる第１カム面２１０ｃのカム角θ１と、第２凹部２１０ｂの底部２１０ｂ１から連結部材２１の周方向に矢印Ａ方向に向かって延びる第２カム面２１０ｄのカム角θ２とが互いに異なり、第１カム面２１０ｃのカム角θ１が第２カム面２１０ｄのカム角θ２よりも大きい。つまり、カム部２１０は、第１凹部２１０ａ及び第２凹部２１０ｂのうち、押圧部材２３による弾性部材２１の押圧方向とは反対側に位置する第１凹部２１０ａの第１カム面２１０ｃのカム角θ１が、押圧方向側に位置する第２凹部２１０ｂの第２カム面２１０ｄのカム角θ２よりも大きい。 Cam portion 210 includes a bottom portion 210a 1 circumferentially in the direction of arrow A cam angle theta 1 of the first cam surface 210c extending toward the (relative rotational direction of the pressing member 23) of the coupling member 21 from the first recess 210a, the Unlike from the bottom 210b 1 of the second recesses 210b and the cam angle theta 2 in the circumferential direction to extend toward the direction of arrow a second cam surface 210d of the connecting member 21 with each other, the cam angle theta 1 of the first cam surface 210c and the second greater than the cam angle theta 2 of the cam surface 210d. That is, the cam portion 210 has a cam angle θ of the first cam surface 210c of the first recess 210a located on the opposite side of the first recess 210a and the second recess 210b from the pressing direction of the elastic member 21 by the pressing member 23. 1 is greater than the cam angle theta 2 of the second cam surface 210d of the second recess 210b located in the pressing direction.

回転力付与機構２ａは、第１カム面２１０ｃのカム角θ１又は第２カム面２１０ｄのカム角θ２と弾性部材２２の付勢力に応じた回転力を押圧部材２３に付与する。突起２３１が第２凹部２１０ｂの底部２１０ｂ１に当接する状態から、回転力付与機構２ａが作動して押圧部材２３が矢印Ａ方向に連結部材２１に対して相対回転すると、突起２３１の先端部２３１ａが第２カム面２１０ｄを摺動し、第１凹部２１０ａの底部２１０ａ１に当接する。これにより、連結部材２１が連結位置から非連結位置まで移動する。 The rotational force applying mechanism 2 a applies a rotational force according to the cam angle θ 1 of the first cam surface 210 c or the cam angle θ 2 of the second cam surface 210 d and the biasing force of the elastic member 22 to the pressing member 23. From the state projections 231 abuts against the bottom portion 210 b 1 of the second recess 210 b, the pressing member 23 rotational force applying mechanism 2a is actuated to rotate relative to the connecting member 21 in the direction of the arrow A, the projection 231 tip 231a There slid second cam surface 210d, to contact the bottom portion 210a 1 of the first recess 210a. Thereby, the connection member 21 moves from the connection position to the non-connection position.

また、突起２３１の先端部２３１ａが第１凹部２１０ａの底部２１０ａ１に当接する状態から、回転力付与機構２ａが作動して押圧部材２３が矢印Ａ方向に連結部材２１に対して相対回転すると、突起２３１の先端部２３１ａが第１カム面２１０ｃを摺動してカム部２１０の頂部２１０ｆを乗り越え、第３カム面２１０ｅを摺動して第２凹部２１０ｂの底部２１０ｂ１に当接する。これにより、連結部材２１が非連結位置から連結位置まで移動する。 Further, from the state tip 231a of the protrusion 231 abuts against the bottom portion 210a 1 of the first recess 210a, the pressing member 23 rotational force applying mechanism 2a is actuated to rotate relative to the connecting member 21 in the arrow A direction, over the top 210f of the cam portion 210 tip 231a of the projection 231 slides the first cam surface 210c, contacts the bottom 210b 1 of the second recess 210b slides the third cam surface 210e. Thereby, the connection member 21 moves from the non-connection position to the connection position.

なお、本実施の形態では、第３カム面２１０ｅのカム角θ３が第１カム面２１０ｃのカム角θ１及び第２カム面２１０ｄのカム角θ２よりも大きく形成されているが、第３カム面２１０ｅのカム角θ３を第２カム面２１０ｄのカム角θ２と同じ角度にしてもよい。カム角θ１〜θ３は、第１乃至第３カム面２１０ｃ，２１０ｄ，２１０ｅが連結部材２１の周方向となす角度であり、図３（ａ）及び（ｂ）では、カム角θ１〜θ３を、第１乃至第３カム面２１０ｃ，２１０ｄ，２１０ｅが連結部材２１の軸方向端面２１ａとの間に形成する角度（劣角）として表している。 In this embodiment, although the cam angle theta 3 of the third cam surface 210e is formed larger than the cam angle theta 2 of the cam angle theta 1 and the second cam surface 210d of the first cam surface 210c, the 3 may be a cam angle theta 3 of the cam surface 210e at the same angle as the cam angle theta 2 of the second cam surface 210d. The cam angles θ 1 to θ 3 are angles formed by the first to third cam surfaces 210c, 210d, and 210e with the circumferential direction of the connecting member 21, and in FIGS. 3A and 3B, the cam angles θ 1 to θ 3 is expressed as an angle (subordinate angle) formed between the first to third cam surfaces 210 c, 210 d, and 210 e and the axial end surface 21 a of the connecting member 21.

前述のように、第１カム面２１０ｃのカム角θ１は第２カム面２１０ｄのカム角θ２よりも大きいので、突起２３１の先端部２３１ａが第１カム面２１０ｃを摺動する際に押圧部材２３が受ける回転抵抗力は、突起２３１の先端部２３１ａが第２カム面２１０ｄを摺動する際に押圧部材２３が受ける回転抵抗力よりも大きい。つまり、突起２３１の先端部２３１ａが第１カム面２１０ｃを摺動する際には、突起２３１の先端部２３１ａが第２カム面２１０ｄを摺動する際に最低限必要な電流よりも大きな電流を電磁コイル２４に供給することが必要となる。 As described above, the cam angle theta 1 of the first cam surface 210c is pressed when is greater than the cam angle theta 2 of the second cam surface 210d, the projections 231 tip 231a slides on the first cam surface 210c The rotational resistance force received by the member 23 is greater than the rotational resistance force received by the pressing member 23 when the tip portion 231a of the protrusion 231 slides on the second cam surface 210d. That is, when the tip 231a of the protrusion 231 slides on the first cam surface 210c, a current larger than the minimum current required when the tip 231a of the protrusion 231 slides on the second cam surface 210d is applied. It is necessary to supply the electromagnetic coil 24.

よって、制御装置４は、突起２３１の先端部２３１ａが第２カム面２１０ｄを摺動することが可能で、かつ突起２３１の先端部２３１ａが第１カム面２１０ｃを摺動することが不可能な範囲の電流値の電流を電磁コイル２４に供給することにより、突起２３１の先端部２３１ａが第１凹部２１０ａの底部２１０ａ１に当接した状態で押圧部材２３と連結部材２１との相対回転を停止させることができる。つまり、制御装置４は、例えば連結部材２１の軸方向の位置を検出可能なセンサからの位置情報を必要とすることなく、電磁コイル２４へ供給する電流の電流値を調節することのみにより、連結部材２１を連結位置から非連結位置に移動させることができる。 Therefore, in the control device 4, the tip portion 231a of the protrusion 231 can slide on the second cam surface 210d, and the tip portion 231a of the protrusion 231 cannot slide on the first cam surface 210c. range current of the current value of by supplying to the electromagnetic coil 24, stop the relative rotation of the pressing member 23 and the connecting member 21 in a state in which the leading end portion 231a of projection 231 abuts the bottom portion 210a 1 of the first recess 210a Can be made. That is, the control device 4 does not require position information from a sensor that can detect the position of the connecting member 21 in the axial direction, for example, and only by adjusting the current value of the current supplied to the electromagnetic coil 24. The member 21 can be moved from the connection position to the non-connection position.

また、制御装置４は、突起２３１の先端部２３１ａが第１カム面２１０ｃを摺動することが可能な電流値の電流を、突起２３１の先端部２３１ａが第１凹部２１０ａの底部２１０ａ１に当接した状態から頂部２１０ｆを乗り越えるために必要な所定時間にわたって電磁コイル２４に供給することで、連結部材２１を非連結位置から連結位置に移動させることができる。この際、突起２３１の先端部２３１ａは、連結部材２１が弾性部材２２から受ける付勢力によって第３カム面２１０ｅを摺動し、第２凹部２１０ｂの底部２１０ｂ１に当接する。 Further, the control unit 4, the current of the current value capable of sliding the distal end portion 231a of the projections 231 is the first cam surface 210c, the leading end portion 231a of projection 231 to the bottom 210a 1 of the first recess 210a equivalent By supplying the electromagnetic coil 24 from the contacted state to the electromagnetic coil 24 for a predetermined time required to get over the top 210f, the connecting member 21 can be moved from the non-connected position to the connected position. At this time, the tip portion 231a of the protrusion 231, coupling member 21 slides the third cam surface 210e by the force applied from the elastic member 22 abuts against the bottom portion 210 b 1 of the second recess 210b.

このように、制御装置４は、クラッチ装置２の連結状態と非連結状態とを切り替える際、突起２３１の先端部２３１ａが第１凹部２１０ａの底部２１０ａ１から第２凹部２１０ｂの底部２１０ｂ１まで移動する間、又は第２凹部２１０ｂの底部２１０ｂ１から第１凹部２１０ａの底部２１０ａ１まで移動する間、電磁コイル２４へ通電すればよく、この移動完了後には、電磁コイル２４への通電を遮断しても、連結状態又は非連結状態が維持される。つまり、連結部材２１は、弾性部材２２によって押圧部材２３側に付勢されているので、この付勢力によって突起２３１の先端部２３１ａが第１凹部２１０ａの底部２１０ａ１又は第２凹部２１０ｂの底部２１０ｂ１に当接した位置で安定的に定位し、この突起２３１の先端部２３１ａが第１凹部２１０ａ又は第２凹部２１０ｂから抜け出すことがない。これにより、制御装置４は、四輪駆動車１の４輪駆動状態又は２輪駆動状態が継続する間は、電磁コイル２４への電流供給を停止することができる。 Thus movement, the control device 4, when switching the connection state of the clutch device 2 and a non-connected state, the tip end portion 231a of the protrusion 231 from the bottom 210a 1 of the first recess 210a to the bottom 210b 1 of the second recess 210b during, or while moving from the bottom 210b 1 of the second recess 210b to the bottom 210a 1 of the first recess 210a, it may be energized to the electromagnetic coil 24, after the completion of the movement, to cut off the energization of the electromagnetic coil 24 However, the connected state or the unconnected state is maintained. That is, the connecting member 21, because it is biased in the pressing member 23 side by the elastic member 22, the distal end portion 231a of the projections 231 by the biasing force bottom 210b of the bottom portion 210a 1 or the second recess 210b of the first recess 210a 1 , the tip 231a of the protrusion 231 does not come out of the first recess 210a or the second recess 210b. Thereby, the control device 4 can stop the current supply to the electromagnetic coil 24 while the four-wheel drive vehicle 1 continues in the four-wheel drive state or the two-wheel drive state.

（第１の実施の形態の作用及び効果）
以上説明した第１の実施の形態によれば、以下に示す作用及び効果が得られる。 (Operation and effect of the first embodiment)
According to the first embodiment described above, the following operations and effects can be obtained.

（１）制御装置４は、クラッチ装置２の連結状態（四輪駆動車１の４輪駆動状態）又はクラッチ装置２の非連結状態（四輪駆動車１の２輪駆動状態）が継続する間は、電磁コイル２４への電流供給を停止することができるので、クラッチ装置２の動作のための消費電力量を削減することができ、電磁コイル２４の温度上昇の抑制を図ることも可能となる。ひいては、長時間にわたって連結状態を維持することが可能である。 (1) While the clutch device 2 is in the connected state (four-wheel drive state of the four-wheel drive vehicle 1) or the clutch device 2 is not connected (two-wheel drive state of the four-wheel drive vehicle 1), the control device 4 continues. Since the current supply to the electromagnetic coil 24 can be stopped, the power consumption for the operation of the clutch device 2 can be reduced, and the temperature rise of the electromagnetic coil 24 can be suppressed. . As a result, it is possible to maintain a connection state over a long time.

（２）第１カム面２１０ｃのカム角θ１は第２カム面２１０ｄのカム角θ２よりも大きいので、制御装置４から電磁コイル２４へ供給する電流を調節することで、突起２３１の先端部２３１ａが第１凹部２１０ａの底部２１０ａ１に当接した状態で押圧部材２３と連結部材２１との相対回転を停止させることができる。これにより、クラッチ装置２を連結状態から非連結状態に移行させる際の制御が容易となる。 (2) Since the cam angle theta 1 of the first cam surface 210c larger than the cam angle theta 2 of the second cam surface 210d, by adjusting the current supplied from the control unit 4 to the electromagnetic coil 24, the tip of the projection 231 the relative rotation of the pressing member 23 and the connecting member 21 can be stopped in a state where part 231a is in contact with the bottom 210a 1 of the first recess 210a. This facilitates control when shifting the clutch device 2 from the connected state to the non-connected state.

（３）回転力付与機構２ａは、電磁ブレーキ機構からなるので、クラッチ装置２の連結状態から非連結状態への移行時、及びクラッチ装置２の非連結状態から連結状態への移行時に、速やかに押圧部材２３を連結部材２１に対して相対回転させる回転力を発生させることができる。 (3) Since the rotational force imparting mechanism 2a is composed of an electromagnetic brake mechanism, when the clutch device 2 shifts from the connected state to the non-connected state, and when the clutch device 2 shifts from the non-connected state to the connected state, it is promptly A rotational force for rotating the pressing member 23 relative to the connecting member 21 can be generated.

（４）突起２３１は、アーマチャ２６に形成された挿通孔２６ａを挿通し、これにより押圧部材２３とアーマチャ２６との相対回転が規制されているので、回転力付与機構２ａが発生する回転力を確実に押圧部材２３に付与することができると共に、クラッチ装置２の構成を簡素化し、装置の小型化にも寄与できる。 (4) Since the protrusion 231 is inserted through the insertion hole 26a formed in the armature 26, and the relative rotation between the pressing member 23 and the armature 26 is restricted thereby, the rotational force generated by the rotational force applying mechanism 2a is generated. While being able to give reliably to the press member 23, the structure of the clutch apparatus 2 is simplified and it can contribute also to size reduction of an apparatus.

（５）連結部材２１は、入力軸部材２０とスプライン係合する第１スプライン係合部２１１を内周面に有し、かつリングギヤ１８２とスプライン係合する第２スプライン係合部２１２を外周面に有しているので、連結部材２１を軸方向移動させることにより、クラッチ装置２の連結状態と非連結状態とを容易に切り替えることが可能である。 (5) The connecting member 21 has a first spline engaging portion 211 that is spline engaged with the input shaft member 20 on the inner peripheral surface, and a second spline engaging portion 212 that is spline engaged with the ring gear 182 on the outer peripheral surface. Therefore, it is possible to easily switch between the connected state and the non-connected state of the clutch device 2 by moving the connecting member 21 in the axial direction.

［第２の実施の形態］
次に、図５及び図６を参照して本発明の第２の実施の形態に係るクラッチ装置２Ａについて説明する。図５は、第２の実施の形態に係るクラッチ装置２Ａ及びその周辺部の構成例を示す断面図である。図６は、第２の実施の形態に係るクラッチ装置２Ａの要部拡大図である。 [Second Embodiment]
Next, a clutch device 2A according to a second embodiment of the present invention will be described with reference to FIGS. FIG. 5 is a cross-sectional view showing a configuration example of the clutch device 2A according to the second embodiment and its peripheral portion. FIG. 6 is an enlarged view of a main part of the clutch device 2A according to the second embodiment.

このクラッチ装置２Ａは、第１の実施の形態に係るクラッチ装置２と同様の機能を有しているが、連結部材２１Ａ及び押圧部材２３Ａならびにアーマチャ２６Ａの構成が、第１の実施の形態に係るクラッチ装置２の連結部材２１及び押圧部材２３ならびにアーマチャ２６の構成と異なる。図５及び図６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、同一の符号を付してその重複した説明を省略する。   The clutch device 2A has the same function as the clutch device 2 according to the first embodiment, but the configuration of the connecting member 21A, the pressing member 23A, and the armature 26A is related to the first embodiment. This is different from the configuration of the connecting member 21, the pressing member 23, and the armature 26 of the clutch device 2. 5 and 6, members and the like that are the same as those described in the first embodiment are denoted by the same reference numerals, and redundant description thereof is omitted.

第１の実施の形態では、連結部材２１にカム部２１０が設けられ、押圧部材２３に突起２３１が設けられていたが、第２の実施の形態では、連結部材２１Ａに突起２１５が設けられ、押圧部材２３Ａにカム部２３０Ａが設けられている。突起２１５及びカム部２３０Ａは、連結部材２１Ａを押圧部材２３Ａに対して軸方向移動させるカム機構を構成する。   In the first embodiment, the cam portion 210 is provided on the connecting member 21 and the protrusion 231 is provided on the pressing member 23. However, in the second embodiment, the protrusion 215 is provided on the connecting member 21A. A cam portion 230A is provided on the pressing member 23A. The protrusion 215 and the cam portion 230A constitute a cam mechanism that moves the connecting member 21A in the axial direction with respect to the pressing member 23A.

連結部材２１Ａは、環状の基部２１０Ａと、基部２１０Ａから押圧部材２３Ａ側に向かって突出した複数の円柱状の突起２１５とを有している。基部２１０Ａは、第１の実施の形態に係る連結部材２１と同様に、入力軸部材２０のスプライン係合部２０１とスプライン係合する第１スプライン係合部２１１を内周面に有し、かつリングギヤ１８２のスプライン係合部１８３とスプライン係合する第２スプライン係合部２１２を外周面に有している。また、基部２１０Ａには、複数の突起２１５が嵌合する穴部２１０ｇが周方向の複数箇所に等間隔に形成されている。突起２１５の先端部２１５ａは半球状であり、突起２１５の基端部２１５ｂは、例えば穴部２１０ｇへの圧入によって基部２１０Ａに固定されている。   The connecting member 21A has an annular base portion 210A and a plurality of columnar protrusions 215 that protrude from the base portion 210A toward the pressing member 23A. 210 A of base parts have the 1st spline engaging part 211 which carries out a spline engagement with the spline engaging part 201 of the input shaft member 20 on an internal peripheral surface similarly to the connection member 21 which concerns on 1st Embodiment, and A second spline engaging portion 212 that engages with the spline engaging portion 183 of the ring gear 182 is provided on the outer peripheral surface. The base 210A has holes 210g into which a plurality of protrusions 215 are fitted at equal intervals in a plurality of locations in the circumferential direction. The tip 215a of the protrusion 215 is hemispherical, and the base end 215b of the protrusion 215 is fixed to the base 210A by press-fitting into the hole 210g, for example.

押圧部材２３Ａは、ヨーク２５の張出部２５１との間に配置された針状スラストころ軸受２９６に当接して軸方向移動が規制されている。押圧部材２３Ａの外周面には、スプライン係合部２３２が形成されている。   The pressing member 23 </ b> A is in contact with a needle-like thrust roller bearing 296 disposed between the overhanging portion 251 of the yoke 25 and is restricted from moving in the axial direction. A spline engaging portion 232 is formed on the outer peripheral surface of the pressing member 23A.

アーマチャ２６Ａは、その内周部に押圧部材２３Ａのスプライン係合部２３２とスプライン係合するスプライン係合部２６１を有している。押圧部材２３Ａは、そのスプライン係合部２３２がアーマチャ２６Ａのスプライン係合部２６１に係合することで、アーマチャ２６Ａに相対回転不能に連結されている。   The armature 26A has a spline engagement portion 261 that engages with the spline engagement portion 232 of the pressing member 23A on the inner peripheral portion thereof. The pressing member 23A is connected to the armature 26A so as not to rotate relative to the armature 26A by the spline engaging portion 232 engaging the spline engaging portion 261 of the armature 26A.

押圧部材２３Ａのカム部２３０Ａにおけるカム面２３０ｂには、弾性部材２２の付勢力を受けた連結部材２１Ａの突起２１５の先端部２５１ａが当接する。押圧部材２３Ａの軸方向におけるカム部２３０Ａの厚さは、周方向の位置によって異なる。カム面２３０ｂは、第１の実施の形態の説明において図４を参照して説明したカム部２１０の第１乃至第３カム面２１０ｃ，２１０ｄ，２１０ｅと同様に形成されている。押圧部材２３Ａが連結部材２１Ａに対して相対回転し、連結部材２１Ａの突起２１５がカム面２３０ｂを摺動することで、連結部材２１Ａは連結位置と非連結位置との間を回転軸線Ｏに沿って軸方向に移動する。これにより、クラッチ装置２Ａの連結状態と非連結状態とが切り替わる。   The distal end portion 251a of the protrusion 215 of the connecting member 21A that receives the urging force of the elastic member 22 contacts the cam surface 230b of the cam portion 230A of the pressing member 23A. The thickness of the cam portion 230A in the axial direction of the pressing member 23A varies depending on the position in the circumferential direction. The cam surface 230b is formed in the same manner as the first to third cam surfaces 210c, 210d, and 210e of the cam portion 210 described with reference to FIG. 4 in the description of the first embodiment. When the pressing member 23A rotates relative to the connecting member 21A and the protrusion 215 of the connecting member 21A slides on the cam surface 230b, the connecting member 21A moves along the rotation axis O between the connected position and the non-connected position. To move in the axial direction. As a result, the connected state and the disconnected state of the clutch device 2A are switched.

本実施の形態によっても、第１の実施の形態について説明した作用及び効果と同様の作用及び効果を得ることができる。   Also according to the present embodiment, it is possible to obtain the same operations and effects as the operations and effects described in the first embodiment.

以上、本発明を第１及び第２の実施の形態に基づいて説明したが、上記に記載した各実施の形態は、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、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り、例えば次に示すように変形してもよい。   As mentioned above, although this invention was demonstrated based on 1st and 2nd embodiment, each embodiment described above does not limit the invention which concerns on a claim. In addition, the present invention can be appropriately modified and implemented without departing from the spirit thereof, and may be modified as shown below, for example.

第１の実施の形態では、第１凹部２１０ａが第２凹部２１０ｂよりも押圧部材２３側に位置している場合について説明したが、これとは逆に、第２凹部２１０ｂが第１凹部２１０ａよりも押圧部材２３側に位置していてもよい。この場合、入力軸部材２０のスプライン係合部２０１は、図２に示す位置よりも弾性部材２２側に設けられ、連結部材２１が押圧部材２３（基部２３０）から離間したときに、連結部材２１の第１スプライン係合部２１１が入力軸部材２０のスプライン係合部２０１にスプライン係合する。   In the first embodiment, the case where the first recess 210a is positioned closer to the pressing member 23 than the second recess 210b has been described. On the contrary, the second recess 210b is more than the first recess 210a. May also be located on the pressing member 23 side. In this case, the spline engaging portion 201 of the input shaft member 20 is provided closer to the elastic member 22 than the position shown in FIG. 2, and when the connecting member 21 is separated from the pressing member 23 (base portion 230), the connecting member 21. The first spline engaging portion 211 is spline engaged with the spline engaging portion 201 of the input shaft member 20.

第１及び第２の実施の形態では、連結部材２１が押圧部材２３からの押圧力を受けて軸方向に移動することにより入力軸部材２０とリングギヤ１８２との連結が解除され、連結部材２１が弾性部材２２の付勢力によって軸方向移動することにより入力軸部材２０とリングギヤ１８２とが連結される場合について説明したが、これとは逆に、連結部材２１が押圧部材２３からの押圧力を受けて軸方向に移動することにより入力軸部材２０とリングギヤ１８２とが連結され、連結部材２１が弾性部材２２の付勢力によって軸方向移動することにより入力軸部材２０とリングギヤ１８２との連結が解除されるように、クラッチ装置２，２Ａを構成してもよい。   In the first and second embodiments, when the connecting member 21 receives the pressing force from the pressing member 23 and moves in the axial direction, the connection between the input shaft member 20 and the ring gear 182 is released, and the connecting member 21 is Although the case where the input shaft member 20 and the ring gear 182 are connected by moving in the axial direction by the urging force of the elastic member 22 has been described, conversely, the connecting member 21 receives a pressing force from the pressing member 23. The input shaft member 20 and the ring gear 182 are connected by moving in the axial direction, and the connection between the input shaft member 20 and the ring gear 182 is released by moving the connecting member 21 in the axial direction by the biasing force of the elastic member 22. In this manner, the clutch devices 2 and 2A may be configured.

第１及び第２の実施の形態では、連結部材２１がリングギヤ１８２と連結位置及び非連結位置において係合し、入力軸部材２０とは連結位置においてのみ係合する場合について説明したが、これとは逆に、連結部材２１が入力軸部材２０と連結位置及び非連結位置において係合し、リングギヤ１８２とは連結位置においてのみ係合するようにクラッチ装置２，２Ａを構成してもよい。この場合、連結部材２１は、常に入力軸部材２０の回転に応じて回転する。   In the first and second embodiments, the connection member 21 is engaged with the ring gear 182 at the connection position and the non-connection position, and the input shaft member 20 is engaged only at the connection position. Conversely, the clutch devices 2 and 2A may be configured such that the connecting member 21 engages with the input shaft member 20 at the connecting position and the non-connecting position, and engages with the ring gear 182 only at the connecting position. In this case, the connecting member 21 always rotates according to the rotation of the input shaft member 20.

第１及び第２の実施の形態では、本発明の第１部材としての入力軸部材２０、及び本発明の第２部材としてのリングギヤ１８２が、共に四輪駆動車１の駆動力伝達系１０における回転部材である場合について説明したが、これに限らず、第１部材又は第２部材が車体等に連結された非回転部材であってもよい。この場合、クラッチ装置２，２Ａは、回転部材の回転を停止させることが可能なブレーキ装置として機能する。   In the first and second embodiments, the input shaft member 20 as the first member of the present invention and the ring gear 182 as the second member of the present invention are both in the driving force transmission system 10 of the four-wheel drive vehicle 1. Although the case where it was a rotation member was demonstrated, not only this but the non-rotation member by which the 1st member or the 2nd member was connected with the vehicle body etc. may be sufficient. In this case, the clutch devices 2 and 2A function as a brake device that can stop the rotation of the rotating member.

また、クラッチ装置２は、四輪駆動車１の駆動力伝達系１０に適用される場合に限らず、例えば工作機械等の各種機械装置に適用することが可能である。   The clutch device 2 is not limited to being applied to the driving force transmission system 10 of the four-wheel drive vehicle 1, but can be applied to various mechanical devices such as machine tools.

１…四輪駆動車、２，２Ａ…クラッチ装置、２ａ…回転力付与機構、３…トルクカップリング、４…制御装置、１０…駆動力伝達系、１１…エンジン、１２…トランスミッション、１３Ｌ…左前輪、１３Ｒ…右前輪、１４Ｌ…左後輪、１４Ｒ…右後輪、１５…フロントディファレンシャル、１６…リヤディファレンシャル、１７…プロペラシャフト、１８，１９…かさ歯車機構、２０…入力軸部材、２１，２１Ａ…連結部材、２１ａ…軸方向端面、２２…弾性部材、２３，２３Ａ…押圧部材、２４…電磁コイル、２５…ヨーク、２５ａ…凹部、２５ｂ…端面、２６，２６Ａ…アーマチャ、２６ａ…挿通孔、２７…プランジャ、３０…ハウジング、３１…インナシャフト、３２…多板クラッチ、３３…電磁コイル、３４…カム機構、４１…第１回転センサ、４２…第２回転センサ、１００…トランスファケース、１０１…第１ケース部材、１０１ａ…内方突起、１０２…第２ケース部材、１５０…フロントデフケース、１５０ａ…筒部、１５１Ｌ，１５１Ｒ…サイドギヤ、１５２…ピニオンギヤ、１５３…ピニオンシャフト、１５４Ｌ，１５４Ｒ…アクスルシャフト、１６０…リヤデフケース、１６１Ｌ，１６１Ｒ…サイドギヤ、１６２…ピニオンギヤ、１６３…ピニオンシャフト、１６３Ｌ，１６３Ｒ…アクスルシャフト、１８１…ドライブピニオン、１８２…リングギヤ、１８３…スプライン係合部、１９１…ピニオンギヤ、１９２…リングギヤ、２０１…スプライン係合部、２１０…カム部、２１０Ａ…基部、２１０ａ…第１凹部、２１０ａ１…底部、２１０ｂ…第２凹部、２１０ｂ１…底部、２１０ｃ…第１カム面、２１０ｄ…第２カム面、２１０ｅ…第３カム面、２１０ｆ…頂部、２１０ｇ…穴部、２１１…第１スプライン係合部、２１２…第２スプライン係合部、２１３…内鍔部、２１４…外鍔部、２１５…突起、２１５ａ…先端部、２１５ｂ…基端部、２３０…基部、２３０Ａ…カム部、２３０ａ…穴部、２３０ｂ…カム面、２３１…突起、２３１ａ…先端部、２３１ｂ…基端部、２３２…スプライン係合部、２５１…張出部、２６１…スプライン係合部、２７０…円筒部、２７１…フランジ部、２８１…スペーサ、２８２…環状支持部材、２９０…シール部材、２９１…第１の玉軸受、２９２…第２の玉軸受、２９３…針状スラストころ軸受、２９４…第１の円錐ころ軸受、２９５…第２の円錐ころ軸受、２９６…針状スラストころ軸受、Ａ…矢印、Ｏ…回転軸線、θ１〜θ３…カム角 DESCRIPTION OF SYMBOLS 1 ... Four-wheel drive vehicle, 2, 2A ... Clutch apparatus, 2a ... Torque-force provision mechanism, 3 ... Torque coupling, 4 ... Control apparatus, 10 ... Driving force transmission system, 11 ... Engine, 12 ... Transmission, 13L ... Left Front wheel, 13R ... right front wheel, 14L ... left rear wheel, 14R ... right rear wheel, 15 ... front differential, 16 ... rear differential, 17 ... propeller shaft, 18, 19 ... bevel gear mechanism, 20 ... input shaft member, 21, 21A: connecting member, 21a: axial end surface, 22: elastic member, 23, 23A ... pressing member, 24 ... electromagnetic coil, 25 ... yoke, 25a ... concave portion, 25b ... end surface, 26, 26A ... armature, 26a ... insertion hole 27 ... Plunger, 30 ... Housing, 31 ... Inner shaft, 32 ... Multi-plate clutch, 33 ... Electromagnetic coil, 34 ... Cam mechanism, 41 ... First Rotation sensor, 42 ... second rotation sensor, 100 ... transfer case, 101 ... first case member, 101a ... inward projection, 102 ... second case member, 150 ... front differential case, 150a ... cylindrical portion, 151L, 151R ... side gear , 152 ... Pinion gear, 153 ... Pinion shaft, 154L, 154R ... Axle shaft, 160 ... Rear differential case, 161L, 161R ... Side gear, 162 ... Pinion gear, 163 ... Pinion shaft, 163L, 163R ... Axle shaft, 181 ... Drive pinion, 182 ... Ring gear, 183 ... Spline engaging part, 191 ... Pinion gear, 192 ... Ring gear, 201 ... Spline engaging part, 210 ... Cam part, 210A ... Base, 210a ... First recess, 210a 1 ... Bottom, 210b ... Second recess 2 10b 1 ... bottom, 210c ... first cam surface, 210d ... second cam surface, 210e ... third cam surface, 210f ... top, 210g ... hole, 211 ... first spline engaging portion, 212 ... second spline engaging Joint part, 213 ... Inner collar part, 214 ... Outer collar part, 215 ... Projection, 215a ... Tip part, 215b ... Base end part, 230 ... Base part, 230A ... Cam part, 230a ... Hole part, 230b ... Cam surface, 231 ... Protrusions, 231a ... Front end part, 231b ... Base end part, 232 ... Spline engaging part, 251 ... Overhang part, 261 ... Spline engaging part, 270 ... Cylinder part, 271 ... Flange part, 281 ... Spacer, 282 Annular support member, 290 ... Seal member, 291 ... First ball bearing, 292 ... Second ball bearing, 293 ... Needle thrust roller bearing, 294 ... First tapered roller bearing, 295 ... Second tapered roller bearing 296 ... needle thrust roller bearings, A ... arrows, O ... Rotation axis, theta 1 through? 3 ... cam angle

Claims (7)

第１部材と第２部材とを係脱可能に連結するクラッチ装置であって、
前記第１部材及び前記第２部材に係合して前記第１部材と前記第２部材とを連結する連結位置、及び前記第１部材と前記第２部材とを相対回転可能とする非連結位置の間を軸方向に進退移動する環状の連結部材と、
前記連結部材を前記軸方向に押圧する押圧部材と、
前記押圧部材を前記連結部材に対して相対回転させる回転力を付与する回転力付与機構とを備え、
前記連結部材及び前記押圧部材のそれぞれの一部は、前記連結部材及び前記押圧部材のうち一方の部材に設けられたカム部と他方の部材に設けられた突起とからなるカム機構を構成し、
前記カム部は、前記連結部材が前記非連結位置にあるときに前記突起の先端部が当接する第１凹部と、前記第１凹部に対して前記軸方向にずれた位置に形成され、前記連結部材が前記連結位置にあるときに前記突起の先端部が当接する第２凹部とを有し、
回転力付与機構の作動によって前記連結部材と前記押圧部材とが相対回転し、前記突起の先端部が前記第１凹部と前記第２凹部との間に形成されたカム面を摺動することで、前記連結部材が前記連結位置と前記非連結位置との間を進退移動する、
クラッチ装置。 A clutch device for releasably connecting a first member and a second member,
A connection position that engages with the first member and the second member to connect the first member and the second member, and a non-connection position that allows the first member and the second member to rotate relative to each other. An annular connecting member that moves forward and backward in the axial direction,
A pressing member that presses the connecting member in the axial direction;
A rotational force applying mechanism for applying a rotational force for rotating the pressing member relative to the connecting member;
A part of each of the connecting member and the pressing member constitutes a cam mechanism including a cam portion provided on one member of the connecting member and the pressing member and a protrusion provided on the other member,
The cam portion is formed at a position where the distal end of the protrusion abuts when the connecting member is in the non-connecting position, and a position shifted in the axial direction with respect to the first recess. A second recess with which the tip of the protrusion abuts when the member is in the coupling position;
By operating the rotational force applying mechanism, the connecting member and the pressing member are rotated relative to each other, and the tip of the protrusion slides on the cam surface formed between the first recess and the second recess. The connecting member moves forward and backward between the connecting position and the non-connecting position;
Clutch device. 前記クラッチ装置は、前記連結部材を前記軸方向に弾性的に付勢し、前記カム部と前記突起とを当接させる弾性部材を備え、
前記押圧部材は、前記連結部材を前記弾性部材の付勢力に抗して押圧し、前記第１凹部の底部から周方向に延びる第１カム面のカム角と、前記第２凹部の底部から周方向に延びる第２カム面のカム角とが互いに異なり、
前記回転力付与機構は、前記第１カム面のカム角又は前記第２カム面のカム角と前記付勢力に応じた回転力を前記押圧部材に付与する、
請求項１に記載のクラッチ装置。 The clutch device includes an elastic member that elastically urges the connecting member in the axial direction to contact the cam portion and the protrusion.
The pressing member presses the connecting member against the urging force of the elastic member, the cam angle of the first cam surface extending in the circumferential direction from the bottom of the first recess, and the periphery from the bottom of the second recess. The cam angles of the second cam surfaces extending in the direction are different from each other,
The rotational force applying mechanism applies a rotational force according to the cam angle of the first cam surface or the cam angle of the second cam surface and the biasing force to the pressing member.
The clutch device according to claim 1. 前記カム部は、前記第１凹部及び前記第２凹部のうち、前記押圧部材による前記弾性部材の押圧方向とは反対側に位置する凹部のカム面のカム角が、前記押圧方向側に位置する凹部のカム角よりも大きい、
請求項２に記載のクラッチ装置。 The cam portion has a cam angle of a cam surface of a concave portion located on a side opposite to a pressing direction of the elastic member by the pressing member among the first concave portion and the second concave portion, and is located on the pressing direction side. Larger than the cam angle of the recess,
The clutch device according to claim 2. 前記回転力付与機構は、通電により磁力を発生する電磁コイルと、前記電磁コイルを支持するヨークと、前記磁力によって前記ヨークに引き寄せられるアーマチャとを有し、前記アーマチャが前記ヨークに引き寄せられることによって発生する摩擦力を前記押圧部材に付与することで、前記押圧部材を前記連結部材に対して相対回転させる、
請求項１乃至３の何れか１項に記載のクラッチ装置。 The rotational force applying mechanism includes an electromagnetic coil that generates a magnetic force when energized, a yoke that supports the electromagnetic coil, and an armature that is attracted to the yoke by the magnetic force, and the armature is attracted to the yoke. By applying the generated frictional force to the pressing member, the pressing member is rotated relative to the connecting member.
The clutch device according to any one of claims 1 to 3. 前記連結部材は、前記第１部材及び前記第２部材のうち一方の部材と前記連結位置及び前記非連結位置において係合し、
前記押圧部材は、前記アーマチャと軸方向に相対移動可能かつ相対回転不能に係合し、
前記回転力付与機構は、前記第１部材又は前記第２部材の回転に応じて回転する前記連結部材と前記押圧部材とを、前記摩擦力によって前記アーマチャの回転を抑制することで相対回転させる、
請求項４に記載のクラッチ装置。 The connecting member engages one of the first member and the second member with the connecting position and the non-connecting position,
The pressing member engages with the armature so as to be relatively movable in the axial direction and non-rotatable.
The rotational force imparting mechanism relatively rotates the coupling member and the pressing member that rotate according to the rotation of the first member or the second member by suppressing the rotation of the armature by the friction force.
The clutch device according to claim 4. 前記突起が前記押圧部材に設けられ、
前記突起が前記アーマチャに形成された挿通孔を挿通している、
請求項５に記載のクラッチ装置。 The protrusion is provided on the pressing member;
The protrusion is inserted through an insertion hole formed in the armature.
The clutch device according to claim 5. 前記連結部材は、前記第１部材とスプライン係合する第１スプライン係合部を内周面に有し、かつ前記第２部材とスプライン係合する第２スプライン係合部を外周面に有する、
請求項１乃至６の何れか１項に記載のクラッチ装置。 The connecting member has a first spline engaging portion that is spline engaged with the first member on an inner peripheral surface, and a second spline engaging portion that is spline engaged with the second member on an outer peripheral surface.
The clutch device according to any one of claims 1 to 6.
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