JP2011144835A - Cam mechanism and electromagnetic clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cam mechanism configured so that deformation of a cam member by cam force can be suppressed, and an electromagnetic clutch provided with the cam mechanism. <P>SOLUTION: The cam mechanism 6 includes: a first cam member 61 having a first cam surface 612a formed to extend in a circumferential direction; a second cam member 62 having a second cam surface 622a formed to face the first cam surface 612a in an axial direction, the second cam member being rotatable relatively to the first cam member 61; and a cam follower 63 disposed between the first cam surface 612a and the second cam surface 622a, the cam follower generating an axial cam force by the relative rotation of the first cam member 61 and the second cam member 62. The second cam member 62 includes a reinforcement portion 623 provided on a side surface 62a on which the second cam surface 622a is formed, the reinforcement portion extending from the inner periphery side of the second cam surface 622a to the outer periphery side to suppress the deformation of the second cam member 62 by the cam force. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、カム機構、及びカム機構を備えた電磁クラッチに関する。   The present invention relates to a cam mechanism and an electromagnetic clutch provided with the cam mechanism.

従来、カム面が形成されたカム部材を電磁コイルの磁力によって吸引し、その吸引により発生する他部材との接触部における摩擦によってカム機構を動作させ、カム機構のカム力によってカム部材をより強く他部材に押し付けることによる摩擦力で回転部材間のトルク伝達を制御する電磁クラッチが知られている。（例えば、特許文献１参照）。   Conventionally, a cam member having a cam surface is attracted by the magnetic force of an electromagnetic coil, the cam mechanism is operated by friction at a contact portion with other members generated by the attraction, and the cam member is made stronger by the cam force of the cam mechanism. 2. Description of the Related Art There is known an electromagnetic clutch that controls torque transmission between rotating members by a frictional force caused by pressing against another member. (For example, refer to Patent Document 1).

特許文献１に記載された電磁クラッチは、前輪をエンジンで駆動し、後輪を電動モータで駆動するように構成された４輪駆動車両の後輪側の駆動系に適用され、電動モータの停止時に後輪のディファレンシャル装置と電動モータとの連結を遮断して走行抵抗を低減すべく、出力軸と減速ギヤ列を構成するギヤとの間に配置されている。   The electromagnetic clutch described in Patent Document 1 is applied to a drive system on the rear wheel side of a four-wheel drive vehicle configured to drive front wheels with an engine and drive rear wheels with an electric motor, and stop the electric motor. Sometimes it is arranged between the output shaft and the gears constituting the reduction gear train in order to cut off the connection between the differential device of the rear wheel and the electric motor to reduce the running resistance.

この電磁クラッチは、電磁コイルと、電磁コイルの磁力によって電磁コイル側に引き寄せられ、出力軸と一体回転する円盤状の部材に摩擦接触するカム部材と、カム部材とギヤとの間に介在するカムフォロアとを備えている。カム部材とギヤとの対向面のそれぞれにはカム面が形成され、カム部材及びギヤはカムフォロアと共にカム機構を構成している。   The electromagnetic clutch includes an electromagnetic coil, a cam member that is attracted to the electromagnetic coil side by the magnetic force of the electromagnetic coil and frictionally contacts a disk-shaped member that rotates integrally with the output shaft, and a cam follower that is interposed between the cam member and the gear. And. A cam surface is formed on each of the facing surfaces of the cam member and the gear, and the cam member and the gear constitute a cam mechanism together with the cam follower.

このカム部材は中心部に出力時を挿通させる挿通孔が形成された円板状であり、カム面が形成された面とは反対側の面に、上記円盤状の部材に摩擦係合する摩擦面が形成されている。この摩擦面は、カム面よりも外周側に形成されている。   This cam member has a disc shape in which an insertion hole for inserting an output is formed at the center, and the friction member that frictionally engages the disc-like member on the surface opposite to the surface on which the cam surface is formed. A surface is formed. The friction surface is formed on the outer peripheral side of the cam surface.

車両の走行時に電磁コイルに通電されると、カム部材は上記円盤状の部材に引き寄せられて摩擦接触し、その摩擦力によってギヤと相対回転する。この相対回転によってカムフォロアがカム面を転動し、カム機構のカム力によってカム部材がより強く円盤状の部材に押し付けられて摩擦係合し、電動モータのトルクがディファレンシャル側に伝達されるようになる。   When the electromagnetic coil is energized during traveling of the vehicle, the cam member is attracted to the disk-shaped member and brought into frictional contact, and is rotated relative to the gear by the frictional force. This relative rotation causes the cam follower to roll on the cam surface, and the cam force of the cam mechanism pushes the cam member more strongly against the disk-shaped member and frictionally engages, so that the torque of the electric motor is transmitted to the differential side. Become.

一方、電磁コイルが非通電の状態で電動モータが停止すると、リターンスプリングの力によってカム機構が中立状態（非作動状態）となり、カム部材の摩擦係合が解除される。これにより電動モータとディファレンシャル装置との連結が遮断される。   On the other hand, when the electric motor is stopped while the electromagnetic coil is not energized, the cam mechanism is neutralized (non-actuated) by the force of the return spring, and the frictional engagement of the cam member is released. As a result, the connection between the electric motor and the differential device is cut off.

特開２００４−１７８０７号公報JP 2004-17807 A

上記のように構成された電磁クラッチのカム部材は、摩擦面よりも内周側に形成されたカム面で軸方向のカム力を受け、摩擦面が摩擦相手部材に摩擦係合する。そのため、カム力によって、摩擦面の内周側を支点として外周側が摩擦相手部材から離間するようにカム部材が弾性変形する。このため、カム部材を摩擦係合させる押圧力は、主として摩擦面の内周側の端部に作用し、極端な場合には外周側が摩擦相手部材から浮いてしまう。ところで、周知のように、トルクＴは物体に加わる力Ｆと回転の軸からみた力の加わる点までの距離ｒとの積（Ｔ＝Ｆ×ｒ）で示されるので、カム部材を摩擦係合させるカム力が作用する部位は、内周側よりも外周側である方が効果的である。   The cam member of the electromagnetic clutch configured as described above receives an axial cam force on the cam surface formed on the inner peripheral side with respect to the friction surface, and the friction surface frictionally engages the friction counterpart member. Therefore, the cam member is elastically deformed by the cam force so that the outer peripheral side is separated from the friction counterpart member with the inner peripheral side of the friction surface as a fulcrum. For this reason, the pressing force for frictionally engaging the cam member mainly acts on the inner peripheral side end of the friction surface, and in the extreme case, the outer peripheral side floats from the friction counterpart member. As is well known, the torque T is indicated by the product (T = F × r) of the force F applied to the object and the distance r to the point where the force is applied as seen from the axis of rotation. The part on which the cam force is applied is more effective on the outer peripheral side than on the inner peripheral side.

しかし、上記のように構成された電磁クラッチのカム部材では、カム力が主として摩擦面の内周側の端部に作用するので、トルク伝達時に摩擦面に滑りを発生させないためにはカム部材の径を大きくしたり、カム部材の周方向に対するカム面の角度を浅くするなどの必要がある。カム部材の径を大きくすると、装置の小型軽量化に限界が生じ、カム面の角度を浅くすると、カム機構の中立位置からカム部材にカム力が発生するまでの相対回転角度が大きくなり、レスポンスが低下する。   However, in the cam member of the electromagnetic clutch configured as described above, the cam force mainly acts on the inner peripheral side end of the friction surface. Therefore, in order to prevent the friction surface from slipping during torque transmission, It is necessary to increase the diameter or to make the angle of the cam surface shallow with respect to the circumferential direction of the cam member. Increasing the diameter of the cam member limits the size and weight of the device, and reducing the cam surface angle increases the relative rotation angle from the neutral position of the cam mechanism until the cam force is generated on the cam member. Decreases.

そこで、本発明は、カム力によるカム部材の変形を抑制することが可能なカム機構、及びカム機構を備えた電磁クラッチを提供することを目的とする。   Accordingly, an object of the present invention is to provide a cam mechanism capable of suppressing deformation of a cam member due to a cam force, and an electromagnetic clutch provided with the cam mechanism.

上記目的を達成するため、本発明のカム機構は、周方向に延びるように形成された第１カム面を有する第１カム部材と、前記第１カム部材との相対回転により軸方向のカム力を発生させる第２カム面が形成された本体部、及び前記第２カム面の内周側と外周側とに亘って径方向に延びるように前記本体部と一体に形成され、前記カム力による前記本体部の変形を抑制する補強部を有する第２カム部材と、を備えている。   In order to achieve the above object, a cam mechanism according to the present invention has a first cam member having a first cam surface formed so as to extend in the circumferential direction and an axial cam force by relative rotation between the first cam member and the first cam member. And is formed integrally with the main body portion so as to extend in the radial direction over the inner peripheral side and the outer peripheral side of the second cam surface. And a second cam member having a reinforcing portion that suppresses deformation of the main body portion.

この構成によれば、補強部がカム力を第２カム面の内周側と外周側で受け、本体部の径方向に伝達する。   According to this configuration, the reinforcing portion receives the cam force on the inner peripheral side and the outer peripheral side of the second cam surface and transmits them in the radial direction of the main body portion.

また、前記第２カム部材は、前記カム面が形成された側面の軸方向反対側の側面に、前記カム力により摩擦相手部材と摩擦係合する摩擦面を有し、前記補強部は、少なくとも一部が前記摩擦面に対応する径方向の範囲に形成されるように構成するとよい。   The second cam member has a friction surface that frictionally engages with a friction counterpart member by the cam force on a side surface opposite to the axial direction of the side surface on which the cam surface is formed, and the reinforcing portion includes at least It is good to comprise so that a part may be formed in the range of the radial direction corresponding to the said friction surface.

この構成によれば、補強部がカム力を第２カム面から摩擦面に伝達する。   According to this configuration, the reinforcing portion transmits the cam force from the second cam surface to the friction surface.

また、前記第２カム部材は、前記本体部に複数の前記第２カム面を有し、前記補強部は、周方向に隣り合う前記第２カム面の間のそれぞれの位置に対応して形成されるように構成するとよい。   The second cam member has a plurality of the second cam surfaces on the main body, and the reinforcing portion is formed corresponding to each position between the second cam surfaces adjacent in the circumferential direction. It is good to constitute as described.

この構成によれば、補強部が複数の第２カム面に発生するカム力を各第２カム面の間の位置から径方向に伝達する。   According to this configuration, the reinforcing portion transmits the cam force generated on the plurality of second cam surfaces from the position between the second cam surfaces in the radial direction.

また、上記目的を達成するため、本発明の電磁クラッチは、周方向に延びるように形成された第１カム面を有する第１カム部材と、前記第１カム部材との相対回転により軸方向のカム力を発生させる第２カム面、及び前記カム力により摩擦相手部材と摩擦係合する摩擦面が形成された本体部を有する第２カム部材と、前記第２カム部材の前記摩擦面を前記摩擦相手部材に接触させるように前記第２カム部材を軸方向移動させる磁力を発生する電磁コイルと、を備え、前記第２カム部材は、前記第２カム面の内周側と外周側とに亘って径方向に延びるように前記本体部と一体に形成され、前記カム力による前記本体部の変形を抑制する補強部を有する。   In order to achieve the above object, an electromagnetic clutch according to the present invention includes a first cam member having a first cam surface formed so as to extend in the circumferential direction, and axial rotation by relative rotation between the first cam member and the first cam member. A second cam member having a second cam surface that generates a cam force, and a main body portion formed with a friction surface that frictionally engages a friction counterpart member by the cam force; and the friction surface of the second cam member is An electromagnetic coil that generates a magnetic force to move the second cam member in the axial direction so as to contact the friction counterpart member, and the second cam member is provided on an inner peripheral side and an outer peripheral side of the second cam surface. And a reinforcing portion that is integrally formed with the main body portion so as to extend in the radial direction and suppresses deformation of the main body portion due to the cam force.

この構成によれば、電磁コイルへの通電により第２カム部材の摩擦面に発生する摩擦力によって第１カム部材と第２カム部材が相対回転し、この相対回転により発生したカム力を補強部が第２カム面の内周側と外周側で受け、本体部の径方向に伝達して摩擦面における摩擦力を増大させる。   According to this configuration, the first cam member and the second cam member are relatively rotated by the frictional force generated on the friction surface of the second cam member by energization of the electromagnetic coil, and the cam force generated by the relative rotation is applied to the reinforcing portion. Is received on the inner peripheral side and the outer peripheral side of the second cam surface and transmitted in the radial direction of the main body portion to increase the frictional force on the friction surface.

本発明によれば、カム力によるカム部材の変形を抑制することができる。   According to the present invention, the deformation of the cam member due to the cam force can be suppressed.

図１は、本発明の第１の実施の形態における４輪駆動車の駆動力伝達系の構成を示す概略図。FIG. 1 is a schematic diagram showing a configuration of a driving force transmission system of a four-wheel drive vehicle according to a first embodiment of the present invention. 図２は、本発明の第１の実施の形態に係るカム機構及び電磁クラッチが適用された駆動力伝達装置の構成を示す断面図。FIG. 2 is a cross-sectional view showing a configuration of a driving force transmission device to which the cam mechanism and the electromagnetic clutch according to the first embodiment of the present invention are applied. 図３は、本発明の第１の実施の形態に係るカム機構の第２カム部材を示す説明図。FIG. 3 is an explanatory view showing a second cam member of the cam mechanism according to the first embodiment of the present invention. 図４は、本発明の第１の実施の形態に係るカム機構の第２カム部材の変形状態を比較例と共に示す説明図。FIG. 4 is an explanatory view showing a deformed state of the second cam member of the cam mechanism according to the first embodiment of the present invention together with a comparative example. 図５は、本発明の第２の実施の形態に係る電磁クラッチの構成を示す概略図。FIG. 5 is a schematic diagram showing a configuration of an electromagnetic clutch according to a second embodiment of the present invention. 図６は、本発明の第２の実施の形態に係るカム機構のカム部材を示す説明図。FIG. 6 is an explanatory view showing a cam member of a cam mechanism according to a second embodiment of the present invention. 図７は、本発明の第３の実施の形態に係るカム機構のカム部材を示す概略図。FIG. 7 is a schematic view showing a cam member of a cam mechanism according to a third embodiment of the present invention.

［第１の実施の形態］
図１は、本発明の第１の実施の形態に係る電磁クラッチが適用された４輪駆動車の駆動力伝達系の概略構成を示す。図１に示すように、４輪駆動車１０１は、駆動源としてのエンジン１０２，エンジン１０２の出力を一対のフロントアクスルシャフト１０４及びプロペラシャフト１０６に分配するトランスアクスル１０３，一対のフロントアクスルシャフト１０４のそれぞれに連結された一対の前輪１０５，プロペラシャフト１０６のトルクをドライブピニオンシャフト１０８に伝達する駆動力伝達装置１，ドライブピニオンシャフト１０８に伝達されたトルクを一対のリヤアクスルシャフト１１０に分配するリヤディファレンシャル１０９，及び一対のリヤアクスルシャフト１１０のそれぞれに連結された一対の後輪１１１を備えている。 [First Embodiment]
FIG. 1 shows a schematic configuration of a driving force transmission system of a four-wheel drive vehicle to which an electromagnetic clutch according to a first embodiment of the present invention is applied. As shown in FIG. 1, a four-wheel drive vehicle 101 includes an engine 102 as a drive source, a transaxle 103 that distributes the output of the engine 102 to a pair of front axle shafts 104 and a propeller shaft 106, and a pair of front axle shafts 104. A driving force transmission device 1 for transmitting the torque of a pair of front wheels 105 and a propeller shaft 106 connected to each to a drive pinion shaft 108, and a rear differential 109 for distributing the torque transmitted to the drive pinion shaft 108 to a pair of rear axle shafts 110. , And a pair of rear wheels 111 connected to each of the pair of rear axle shafts 110.

駆動力伝達装置１は、４輪駆動車１０１の車体（図示せず）に固定されたディファレンシャルキャリア１０７を介してその内部に支持され、プロペラシャフト１０６とドライブピニオンシャフト１０８とのトルク伝達を制御可能に構成されている。駆動力伝達装置１がプロペラシャフト１０６とドライブピニオンシャフト１０８とをトルク伝達可能に連結すると４輪駆動車１０１が４輪駆動状態となり、この連結を解除すると４輪駆動車１０１が２輪駆動状態となる。   The driving force transmission device 1 is supported inside a differential carrier 107 fixed to a vehicle body (not shown) of the four-wheel drive vehicle 101, and can control torque transmission between the propeller shaft 106 and the drive pinion shaft 108. It is configured. When the driving force transmission device 1 connects the propeller shaft 106 and the drive pinion shaft 108 so that torque can be transmitted, the four-wheel drive vehicle 101 enters a four-wheel drive state, and when this connection is released, the four-wheel drive vehicle 101 enters a two-wheel drive state. Become.

また、４輪駆動車１０１には、駆動力伝達装置１を制御するコントローラ１１２が搭載されている。コントローラ１１２は、一対の前輪１０５及び一対の後輪１１１の回転速度やアクセル開度等に基づいて駆動力伝達装置１に電流を供給し、駆動力伝達装置１のトルク伝達を制御する。   The four-wheel drive vehicle 101 is equipped with a controller 112 that controls the driving force transmission device 1. The controller 112 supplies current to the driving force transmission device 1 based on the rotational speeds of the pair of front wheels 105 and the pair of rear wheels 111, the accelerator opening degree, and the like, and controls torque transmission of the driving force transmission device 1.

（駆動力伝達装置１の全体構成）
図２は駆動力伝達装置１の構成を示す断面図である。この駆動力伝達装置１は、ディファレンシャルキャリア１０７（図１に示す）に対して回転軸Ｏの周りに回転可能なハウジング２と、このハウジング２に対して同軸状で相対回転可能なインナシャフト３と、ハウジング２とインナシャフト３との間に配置されたメインクラッチ４と、ディファレンシャルキャリア１０７に対して回転不能に保持された電磁コイル５と、電磁コイル５の通電によって作動し、メインクラッチ４を押圧するカム力を発生するカム機構６とから大略構成されている。電磁コイル５及びカム機構６は、電磁クラッチ１０を構成する。 (Overall configuration of the driving force transmission device 1)
FIG. 2 is a cross-sectional view illustrating a configuration of the driving force transmission device 1. The driving force transmission device 1 includes a housing 2 that can rotate around a rotation axis O with respect to a differential carrier 107 (shown in FIG. 1), and an inner shaft 3 that is coaxial and relatively rotatable with respect to the housing 2. The main clutch 4 disposed between the housing 2 and the inner shaft 3, the electromagnetic coil 5 held non-rotatable with respect to the differential carrier 107, and the electromagnetic coil 5 are energized to press the main clutch 4. And a cam mechanism 6 that generates a cam force. The electromagnetic coil 5 and the cam mechanism 6 constitute an electromagnetic clutch 10.

（ハウジング２の構成）
ハウジング２は、フロントハウジング２１、及びフロントハウジング２１と一体回転するように結合されたリヤハウジング２２からなり、ディファレンシャルキャリア１０７の内部に軸受（図示せず）を介して支持されている。 (Configuration of housing 2)
The housing 2 includes a front housing 21 and a rear housing 22 coupled so as to rotate integrally with the front housing 21, and is supported inside the differential carrier 107 via a bearing (not shown).

フロントハウジング２１は、例えば非磁性体材料であるアルミニウム合金からなり、リヤハウジング２２側に開口する収容空間２１ａ、及びこの収容空間２１ａの内面に形成されたストレートスプライン嵌合部２１ｂを有し、プロペラシャフト１０６（図１に示す）と一体回転するように連結されている。収容空間２１ａには潤滑油が約８０％の充填率で充填されている。   The front housing 21 is made of, for example, an aluminum alloy that is a nonmagnetic material, and includes a housing space 21a that opens to the rear housing 22 side, and a straight spline fitting portion 21b that is formed on the inner surface of the housing space 21a. The shaft 106 (shown in FIG. 1) is connected to rotate integrally. The accommodating space 21a is filled with lubricating oil at a filling rate of about 80%.

リヤハウジング２２は、フロントハウジング２１の開口内周面に螺着された炭素鋼（例えばＳ３５Ｃ、Ｓ１０Ｃ）等の磁性材料からなる外側部材２２１と、外側部材２２１の内側に溶接等によって一体に結合されたステンレス等の非磁性材料からなる中間部材２２２と、中間部材２２２の内側に溶接等によって一体に結合された炭素鋼等の磁性材料からなる内側部材２２３とからなる。   The rear housing 22 is integrally coupled to the outer member 221 made of a magnetic material such as carbon steel (for example, S35C, S10C) screwed to the inner peripheral surface of the opening of the front housing 21 and the inner side of the outer member 221 by welding or the like. An intermediate member 222 made of a non-magnetic material such as stainless steel, and an inner member 223 made of a magnetic material such as carbon steel integrally joined to the inside of the intermediate member 222 by welding or the like.

リヤハウジング２２には、フロントハウジング２１の収容空間２１ａの開口方向と同一の方向に開口する円環状の収容空間２２ａが形成されている。また、リヤハウジング２２の収容空間２２ａとは反対側の側面には、後述する第２カム部材６２と摩擦係合する摩擦面２２ｂが形成されている。   The rear housing 22 is formed with an annular housing space 22 a that opens in the same direction as the opening direction of the housing space 21 a of the front housing 21. Further, a friction surface 22b that frictionally engages a second cam member 62 described later is formed on the side surface of the rear housing 22 opposite to the accommodation space 22a.

（インナシャフト３の構成）
インナシャフト３は、フロントハウジング２１との間に介在するボール軸受２１０、及びリヤハウジング２２との間に介在するニードル軸受２２０によって、ハウジング２の内側に支持されている。 (Configuration of inner shaft 3)
The inner shaft 3 is supported inside the housing 2 by a ball bearing 210 interposed between the front housing 21 and a needle bearing 220 interposed between the rear housing 22.

インナシャフト３は、リヤハウジング２２側の端面３ａから軸方向に延びる第１の中空部３ｂが形成され、第１の中空部３ｂの内面には、ストレートスプライン嵌合部３ｃが設けられている。第１の中空部３ｂには、ドライブピニオンシャフト１０８（図１に示す）の先端部が挿入され、ドライブピニオンシャフト１０８の先端部に形成されたストレートスプライン嵌合部（図示せず）が第１の中空部３ｂのストレートスプライン嵌合部３ｃに嵌合する。   The inner shaft 3 is formed with a first hollow portion 3b extending in the axial direction from the end surface 3a on the rear housing 22 side, and a straight spline fitting portion 3c is provided on the inner surface of the first hollow portion 3b. The first hollow portion 3b is inserted with the tip of a drive pinion shaft 108 (shown in FIG. 1), and a straight spline fitting portion (not shown) formed at the tip of the drive pinion shaft 108 is the first. It fits into the straight spline fitting part 3c of the hollow part 3b.

また、インナシャフト３には、フロントハウジング２１側の端面３ｄから軸方向に延びる第２の中空部３ｅが形成され、この第２の中空部３ｅには潤滑油が収容される。第１の中空部３ｂと第２の中空部３ｅとは壁部３ｆによって分離されている。   Further, the inner shaft 3 is formed with a second hollow portion 3e extending in the axial direction from the end surface 3d on the front housing 21 side, and lubricating oil is accommodated in the second hollow portion 3e. The first hollow portion 3b and the second hollow portion 3e are separated by a wall portion 3f.

また、インナシャフト３の外面には、フロントハウジング２１のストレートスプライン嵌合部２１ｂと対向する部位に、ストレートスプライン嵌合部３ｇが形成されている。   Further, on the outer surface of the inner shaft 3, a straight spline fitting portion 3g is formed at a portion facing the straight spline fitting portion 21b of the front housing 21.

（メインクラッチ４の構成）
メインクラッチ４は、複数のアウタクラッチプレート４１、及びアウタクラッチプレート４１と交互に配置された複数のインナクラッチプレート４２を有し、潤滑油が充填された収容空間２１ａ内で両クラッチプレートが摺動する湿式の多板クラッチとして構成されている。 (Configuration of main clutch 4)
The main clutch 4 has a plurality of outer clutch plates 41 and a plurality of inner clutch plates 42 arranged alternately with the outer clutch plates 41, and both the clutch plates slide in an accommodation space 21a filled with lubricating oil. It is configured as a wet multi-plate clutch.

アウタクラッチプレート４１は、その外周部にスプライン嵌合部４１ａを有し、スプライン嵌合部４１ａがフロントハウジング２１のストレートスプライン嵌合部２１ｂに嵌合している。これにより、アウタクラッチプレート４１は、ハウジング２に対して軸方向移動可能で、ハウジング２と一体回転するように連結されている。   The outer clutch plate 41 has a spline fitting portion 41 a on the outer periphery thereof, and the spline fitting portion 41 a is fitted to the straight spline fitting portion 21 b of the front housing 21. As a result, the outer clutch plate 41 is axially movable with respect to the housing 2 and is connected to rotate integrally with the housing 2.

インナクラッチプレート４２は、その内周部にスプライン嵌合部４２ａを有し、スプライン嵌合部４２ａがインナシャフト３のストレートスプライン嵌合部３ｇに嵌合している。これにより、インナクラッチプレート４２は、インナシャフト３に対して軸方向移動可能で、インナシャフト３と一体回転するように連結されている。また、インナクラッチプレート４２には、潤滑油を流通させるための孔４２ｂが周方向の複数の箇所に形成されている。   The inner clutch plate 42 has a spline fitting portion 42 a on its inner peripheral portion, and the spline fitting portion 42 a is fitted to the straight spline fitting portion 3 g of the inner shaft 3. Thereby, the inner clutch plate 42 is axially movable with respect to the inner shaft 3 and is connected so as to rotate integrally with the inner shaft 3. Further, the inner clutch plate 42 has holes 42b through which lubricating oil is circulated at a plurality of locations in the circumferential direction.

（電磁コイル５の構成）
電磁コイル５は、ディファレンシャルキャリア１０７（図１に示す）に固定された炭素鋼等の磁性材料からなるヨーク５１に保持されて、リヤハウジング２２の収容空間２２ａ内に配置されている。ヨーク５１は、リヤハウジング２２の外側部材２２１の内周面との間にエアギャップ５１ａを、内側部材２２３との間にエアギャップ５１ｂをそれぞれ介在させて、内側部材２２３との間に設けられたシール軸受５２を介してリヤハウジング２２を支持している。 (Configuration of electromagnetic coil 5)
The electromagnetic coil 5 is held by a yoke 51 made of a magnetic material such as carbon steel fixed to a differential carrier 107 (shown in FIG. 1), and is disposed in a housing space 22 a of the rear housing 22. The yoke 51 is provided between the inner member 223 with an air gap 51a interposed between the yoke 51 and the inner peripheral surface of the outer member 221 of the rear housing 22 and an air gap 51b between the inner member 223 and the inner member 223. The rear housing 22 is supported via a seal bearing 52.

ヨーク５１には、収容空間２２ａの軸方向の底部側に向かって開口した環状の収容空間５１ｃが形成され、この収容空間５１ｃに電磁コイル５が保持されている。電磁コイル５の巻線には、ヨーク５１に形成された孔５１ｄに挿通された電線５ａから供給される電流が通電される。   The yoke 51 is formed with an annular storage space 51c that opens toward the bottom in the axial direction of the storage space 22a, and the electromagnetic coil 5 is held in the storage space 51c. A current supplied from an electric wire 5 a inserted through a hole 51 d formed in the yoke 51 is energized in the winding of the electromagnetic coil 5.

（カム機構６の構成）
カム機構６は、メインクラッチ４とリヤハウジング２２との間に配置され、第１カム部材６１と、第２カム部材６２と、第１カム部材６１及び第２カム部材６２の間に介在する球状のカムフォロア６３とを有して構成されている。第１カム部材６１はカムフォロア６３よりもメインクラッチ４の側に配置され、第２カム部材６２はカムフォロア６３よりもリヤハウジング２２の側に配置されている。 (Configuration of cam mechanism 6)
The cam mechanism 6 is disposed between the main clutch 4 and the rear housing 22, and has a spherical shape interposed between the first cam member 61, the second cam member 62, and the first cam member 61 and the second cam member 62. The cam follower 63 is configured. The first cam member 61 is disposed closer to the main clutch 4 than the cam follower 63, and the second cam member 62 is disposed closer to the rear housing 22 than the cam follower 63.

（第１カム部材６１の構成）
第１カム部材６１は、炭素鋼等の金属材料からなる環状の部材であり、インナシャフト３に外嵌されている。第１カム部材６１は、メインクラッチ４の側に設けられた押圧部６１１と、カムフォロア６３の側に設けられたカム部６１２とが一体に形成されている。押圧部６１１には、メインクラッチ４の複数のインナクラッチプレート４２のうち、最もカム機構６側に位置するインナクラッチプレート４２に対向する押圧面６１１ａが形成されている。カム部６１２には、カムフォロア６３が転動する複数の第１カム面６１２ａが形成されている。 (Configuration of the first cam member 61)
The first cam member 61 is an annular member made of a metal material such as carbon steel, and is externally fitted to the inner shaft 3. The first cam member 61 is integrally formed with a pressing portion 611 provided on the main clutch 4 side and a cam portion 612 provided on the cam follower 63 side. The pressing portion 611 is formed with a pressing surface 611 a that faces the inner clutch plate 42 that is located closest to the cam mechanism 6 among the plurality of inner clutch plates 42 of the main clutch 4. The cam portion 612 is formed with a plurality of first cam surfaces 612a on which the cam follower 63 rolls.

第１カム部材６１の押圧部６１１の内周側には、ストレートスプライン嵌合部６１１ｂが形成され、このストレートスプライン嵌合部６１１ｂはインナシャフト３のストレートスプライン嵌合部３ｇに嵌合されている。これにより、第１カム部材６１はインナシャフト３に対して相対回転不能かつ軸方向移動可能である。また、第１カム部材６１は、インナシャフト３のストレートスプライン嵌合部３ｇのリヤハウジング２２側に形成された段差部３ｈとカム部６２２との間に配置された皿バネ６４によって第２カム部材６２に向かう方向に付勢されている。   A straight spline fitting portion 611 b is formed on the inner peripheral side of the pressing portion 611 of the first cam member 61, and this straight spline fitting portion 611 b is fitted to the straight spline fitting portion 3 g of the inner shaft 3. . Accordingly, the first cam member 61 is not rotatable relative to the inner shaft 3 and is movable in the axial direction. Further, the first cam member 61 is a second cam member by a disc spring 64 disposed between a step portion 3 h formed on the rear housing 22 side of the straight spline fitting portion 3 g of the inner shaft 3 and the cam portion 622. It is urged in the direction toward 62.

（第２カム部材６２の構成）
第２カム部材６２は、例えばプレス加工により成形された炭素鋼等の磁性材料からなる環状の部材であり、その中心部にインナシャフト３を挿通させる挿通孔６２ｃが形成され、インナシャフト３に対して軸方向移動可能に外嵌されている。第２カム部材６２は、本体部６２０と補強部６２３とが一体に形成されている。 (Configuration of the second cam member 62)
The second cam member 62 is an annular member made of a magnetic material such as carbon steel formed by press working, for example, and an insertion hole 62c through which the inner shaft 3 is inserted is formed at the center thereof. And is fitted so as to be movable in the axial direction. The second cam member 62 includes a body portion 620 and a reinforcing portion 623 that are integrally formed.

本体部６２０は、リヤハウジング２２の摩擦面２２ｂと摩擦係合する摩擦面６２１ａが形成された摩擦部６２１と、カムフォロア６３が転動する第２カム面６２２ａが形成されたカム部６２２とから構成されている。摩擦部６２１は、カム部６２２の外周側に形成されている。   The main body 620 includes a friction part 621 formed with a friction surface 621a that frictionally engages the friction surface 22b of the rear housing 22, and a cam part 622 formed with a second cam surface 622a on which the cam follower 63 rolls. Has been. The friction part 621 is formed on the outer peripheral side of the cam part 622.

補強部６２３は、摩擦部６２１及びカム部６２２に亘って、本体部６２０の摩擦面６２１ａとは軸方向反対側の側面６２ａに形成されている。補強部６２３の構成については後述する。   The reinforcing portion 623 is formed on the side surface 62 a opposite to the friction surface 621 a of the main body portion 620 across the friction portion 621 and the cam portion 622. The configuration of the reinforcing portion 623 will be described later.

第２カム部材６２は、電磁コイル５への通電時に発生する磁力によってリヤハウジング２２に引き寄せられるように軸方向に移動し、摩擦部６２１の摩擦面６２１ａがリヤハウジング２２の摩擦面２２ｂと摩擦係合するように構成されている。また、第２カム部材６２は皿バネ６５により第１カム部材６１に向かう方向に付勢されている。皿バネ６５は、インナシャフト３の外周面に嵌着されたスナップリング６６により軸方向移動が規制されている。   The second cam member 62 moves in the axial direction so as to be attracted to the rear housing 22 by the magnetic force generated when the electromagnetic coil 5 is energized, and the friction surface 621a of the friction portion 621 is frictionally engaged with the friction surface 22b of the rear housing 22. Configured to match. Further, the second cam member 62 is biased in a direction toward the first cam member 61 by a disc spring 65. The disc spring 65 is restricted from moving in the axial direction by a snap ring 66 fitted to the outer peripheral surface of the inner shaft 3.

（カムフォロア６３の構成）
カムフォロア６３は、炭素鋼等の金属材料からなり、第１カム部材６１の第１カム面６１２ａと第２カム部材６２の第２カム面６２２ａとの間に挟持され、第１カム面６１２ａ及び第２カム面６２２ａを転動する。第１カム部材６１と第２カム部材６２は、カムフォロア６３が第１カム面６１２ａ及び第２カム面６２２ａを転動する範囲において相対回転が可能である。 (Configuration of cam follower 63)
The cam follower 63 is made of a metal material such as carbon steel, and is sandwiched between the first cam surface 612a of the first cam member 61 and the second cam surface 622a of the second cam member 62, and the first cam surface 612a and the first cam surface 612a. 2 Rolls on the cam surface 622a. The first cam member 61 and the second cam member 62 are capable of relative rotation within a range in which the cam follower 63 rolls on the first cam surface 612a and the second cam surface 622a.

第１カム面６１２ａ及び第２カム面６２２ａは周方向に延びるように形成され、その中央部における軸方向の深さが最も深く、周方向の端部に向かうにつれて浅くなるように形成されている。従って、第１カム部材６１に対して第２カム部材６２が相対回転し、カムフォロア６３が第１カム面６１２ａ及び第２カム面６２２ａの周方向の中央部の位置（中立位置）から転動すると、第２カム部材に第１カム部材６１から軸方向に離間するカム力が発生する。   The first cam surface 612a and the second cam surface 622a are formed so as to extend in the circumferential direction, and are formed so that the depth in the axial direction at the center is the deepest and becomes shallower toward the end in the circumferential direction. . Accordingly, when the second cam member 62 rotates relative to the first cam member 61 and the cam follower 63 rolls from the position (neutral position) of the first cam surface 612a and the second cam surface 622a in the circumferential direction. The second cam member generates a cam force that is separated from the first cam member 61 in the axial direction.

第１カム面６１２ａ及び第２カム面６２２ａは、第１カム部材６１及び第２カム部材６２の周方向の複数の箇所に形成され、そのそれぞれにカムフォロア６３が配置されている。   The first cam surface 612a and the second cam surface 622a are formed at a plurality of locations in the circumferential direction of the first cam member 61 and the second cam member 62, and the cam follower 63 is disposed at each of the locations.

（第２カム部材６２の補強部６２３の構成）
図３は、側面６２ａの側から見た第２カム部材６２の形状を示す。この図では、リヤハウジング２２の摩擦面２２ｂ（図２に示す）と摩擦係合する摩擦面６２１ａの内周円６２１ｂを破線で示す。 (Configuration of the reinforcing portion 623 of the second cam member 62)
FIG. 3 shows the shape of the second cam member 62 as viewed from the side surface 62a. In this figure, the inner circumferential circle 621b of the friction surface 621a that frictionally engages the friction surface 22b (shown in FIG. 2) of the rear housing 22 is indicated by a broken line.

第２カム部材６２のカム部６２２には、６つの第２カム面６２２ａが等間隔に配置されている。各第２カム面６２２ａは、第２カム部材６２の周方向に沿って湾曲する円弧状に形成されている。周方向に隣り合う２つの第２カム面６２２ａの間には、カム面が形成されていない非形成領域６２２ｂ（図３に二点鎖線で一箇所のみ示す）が設けられている。   Six second cam surfaces 622 a are arranged at equal intervals on the cam portion 622 of the second cam member 62. Each second cam surface 622 a is formed in an arc shape that curves along the circumferential direction of the second cam member 62. Between the two second cam surfaces 622a adjacent to each other in the circumferential direction, a non-formation region 622b (only one location is indicated by a two-dot chain line in FIG. 3) where no cam surface is formed is provided.

側面６２ａには、内周側から外周側に向かって延在する、第２カム面６２２ａと同数（６つ）の補強部６２３が設けられている。補強部６２３は、補強部６２３が設けられていない領域６２ｂよりも第２カム部材６２の軸方向の厚みを厚く形成することにより、第２カム部材６２と一体に設けられている。   The side surface 62a is provided with the same number (six) of reinforcing portions 623 as the second cam surface 622a extending from the inner peripheral side toward the outer peripheral side. The reinforcing portion 623 is provided integrally with the second cam member 62 by forming the second cam member 62 to be thicker in the axial direction than the region 62b where the reinforcing portion 623 is not provided.

補強部６２３が設けられた箇所の第２カム部材６２の軸方向の厚みは、補強部６２３が設けられていない領域６２ｂの軸方向の厚みの１．２から２．０倍とすることが好ましい。１．２倍以下では第２カム部材６２の変形を抑制する効果が十分ではなく、２．０倍以上では第１カム部材６１との干渉が生じ、また第２カム部材６２の質量が大きくなって電磁コイル５の磁力による軸方向の移動速度が低下するからである。   The axial thickness of the second cam member 62 where the reinforcing portion 623 is provided is preferably 1.2 to 2.0 times the axial thickness of the region 62b where the reinforcing portion 623 is not provided. . If it is 1.2 times or less, the effect of suppressing the deformation of the second cam member 62 is not sufficient, and if it is 2.0 times or more, interference with the first cam member 61 occurs, and the mass of the second cam member 62 increases. This is because the moving speed in the axial direction due to the magnetic force of the electromagnetic coil 5 decreases.

補強部６２３は、非形成領域６２２ｂを含む領域に設けられ、補強部６２３の内周側の端部６２３ａは、第２カム面６２２ａの径方向の中心位置６２２ｃよりも内周側に位置している。また、補強部６２３の外周側の端部６２３ｂは、摩擦面６２１ａの内周円６２１ｂよりも外周側に位置している。このように、補強部６２３は、第２カム面６２２ａの内周側と外周側とに亘って径方向に延びるように形成されている。   The reinforcing portion 623 is provided in a region including the non-formation region 622b, and an end portion 623a on the inner peripheral side of the reinforcing portion 623 is located on the inner peripheral side with respect to the center position 622c in the radial direction of the second cam surface 622a. Yes. Moreover, the outer peripheral end 623b of the reinforcing portion 623 is located on the outer peripheral side of the inner peripheral circle 621b of the friction surface 621a. Thus, the reinforcement part 623 is formed so that it may extend in radial direction over the inner peripheral side and outer peripheral side of the 2nd cam surface 622a.

（駆動力伝達装置１の動作）
次に、駆動力伝達装置１の動作を説明する。４輪駆動車１０１のエンジン１０２が始動していない状態では、カム機構６は非作動状態であり、第１カム部材６１及び第２カム部材６２は、皿バネ６４及び皿バネ６５の付勢力により相互に接近した状態にある。 (Operation of the driving force transmission device 1)
Next, the operation of the driving force transmission device 1 will be described. When the engine 102 of the four-wheel drive vehicle 101 is not started, the cam mechanism 6 is in an inoperative state, and the first cam member 61 and the second cam member 62 are driven by the urging force of the disc spring 64 and the disc spring 65. They are close to each other.

エンジン１０２が始動し、４輪駆動車１０１が発進する際には、前輪及び後輪を駆動する４輪駆動状態とすべく、コントローラ１１２が駆動力伝達装置１の電磁コイル５に電流を供給し、通電する。この通電により、図２に点線で示すように、ヨーク５１，リヤハウジング２２の外側部材２２１，第２カム部材６２，及びリヤハウジング２２の内側部材２２３により形成される磁路に磁束Ｍが発生し、この磁力によって第２カム部材６２がリヤハウジング２２側に向かって軸方向移動し、第２カム部材６２の摩擦面６２１ａとリヤハウジング２２の摩擦面２２ｂとが摩擦接触する。   When the engine 102 starts and the four-wheel drive vehicle 101 starts, the controller 112 supplies a current to the electromagnetic coil 5 of the driving force transmission device 1 so as to set the four-wheel drive state in which the front wheels and the rear wheels are driven. Energize. This energization generates a magnetic flux M in a magnetic path formed by the yoke 51, the outer member 221 of the rear housing 22, the second cam member 62, and the inner member 223 of the rear housing 22, as indicated by a dotted line in FIG. Due to this magnetic force, the second cam member 62 moves in the axial direction toward the rear housing 22, and the friction surface 621 a of the second cam member 62 and the friction surface 22 b of the rear housing 22 come into frictional contact.

この状態でハウジング２とインナシャフト３が差動回転すると、カムフォロア６３が第１カム面６１２ａ及び第２カム面６２２ａを転動し、第１カム部材６１と第２カム部材６２とを軸方向に離間させるカム力が発生する。このカム力により第２カム部材６２はリヤハウジング２２に押し付けられて摩擦係合し、第１カム部材６１はメインクラッチ４を押圧する。第１カム部材６１がメインクラッチ４を押圧することでアウタクラッチプレート４１とインナクラッチプレート４２とが摩擦係合してトルク伝達可能な状態となり、プロペラシャフト１０６を介して伝達されたエンジン１０２のトルクがドライブピニオンシャフト１０８に伝達され、４輪駆動状態となる。   When the housing 2 and the inner shaft 3 are differentially rotated in this state, the cam follower 63 rolls on the first cam surface 612a and the second cam surface 622a, and the first cam member 61 and the second cam member 62 are moved in the axial direction. A cam force for separating is generated. By this cam force, the second cam member 62 is pressed against the rear housing 22 and frictionally engaged, and the first cam member 61 presses the main clutch 4. When the first cam member 61 presses the main clutch 4, the outer clutch plate 41 and the inner clutch plate 42 are frictionally engaged to transmit torque, and the torque of the engine 102 transmitted via the propeller shaft 106 is obtained. Is transmitted to the drive pinion shaft 108 to be in a four-wheel drive state.

また、コントローラ１１２は、例えば４輪駆動車１０１が一定の車速で直進する定常走行状態となると、燃費向上のために一対の前輪１０５のみを駆動する２輪駆動状態とすべく、電磁コイル５への通電を遮断する。   Further, for example, when the four-wheel drive vehicle 101 is in a steady running state in which the four-wheel drive vehicle 101 goes straight at a constant vehicle speed, the controller 112 supplies the electromagnetic coil 5 to a two-wheel drive state in which only the pair of front wheels 105 are driven to improve fuel efficiency. Shut off the power of the.

電磁コイル５への通電が遮断されると、皿バネ６５の付勢力によって第２カム部材６２がリヤハウジング２２から離間する。すると、第１カム部材６１と第２カム部材６２とを相対回転させる力がなくなり、カムフォロア６３が中立位置に転動してカム機構６が非作動状態となる。そして、皿バネ６４の付勢力によって第２カム部材６２がメインクラッチ４を押圧しない位置に戻される。これにより、アウタクラッチプレート４１とインナクラッチプレート４２との摩擦係合が解除され、２輪駆動状態となる。   When the energization of the electromagnetic coil 5 is interrupted, the second cam member 62 is separated from the rear housing 22 by the biasing force of the disc spring 65. Then, there is no force to relatively rotate the first cam member 61 and the second cam member 62, the cam follower 63 rolls to the neutral position, and the cam mechanism 6 becomes inoperative. Then, the second cam member 62 is returned to a position where the main clutch 4 is not pressed by the biasing force of the disc spring 64. As a result, the frictional engagement between the outer clutch plate 41 and the inner clutch plate 42 is released, and a two-wheel drive state is established.

また、例えば４輪駆動車１０１の一対の前輪１０５の何れかにスリップが発生したこと等により、コントローラ１１２が電磁コイル５への通電を再開すると、第２カム部材６２がリヤハウジング２２に引き寄せられ、カム機構６が作動し、メインクラッチ４がトルク伝達可能な状態となって、４輪駆動車１０１が４輪駆動状態となる。   Further, when the controller 112 resumes energization to the electromagnetic coil 5 due to, for example, a slip occurring in one of the pair of front wheels 105 of the four-wheel drive vehicle 101, the second cam member 62 is attracted to the rear housing 22. Then, the cam mechanism 6 operates, the main clutch 4 is in a state where torque can be transmitted, and the four-wheel drive vehicle 101 enters the four-wheel drive state.

（第１の実施の形態の作用）
図４は、カム機構の作動時及び非作動時における第２カム部材の形状の変化を示し、（ａ）は、本実施の形態に係る第２カム部材６２及びその周辺部を、（ｂ）は、比較例としての、補強部を有していない第２カム部材２００及びその周辺部を示す。この第２カム部材２００は、補強部を有していない他は第２カム部材６２と同様に構成され、摩擦面２０１ａを有する摩擦部２０１と、カムフォロア６３が転動するカム面２０２ａを有するカム部２０２とが一体に形成されている。また、図４では、第２カム部材６２及び第２カム部材２００のカム機構の非作動時における断面形状の輪郭を二点鎖線で、作動時における断面形状の輪郭を実線で、それぞれ示す。なお、この図では説明のために第２カム部材６２及び第２カム部材２００の変形量を誇張して表している。 (Operation of the first embodiment)
4A and 4B show changes in the shape of the second cam member when the cam mechanism is operated and when the cam mechanism is not operated. FIG. 4A shows the second cam member 62 and its peripheral portion according to the present embodiment. These show the 2nd cam member 200 which does not have a reinforcement part as a comparative example, and its peripheral part. The second cam member 200 is configured in the same manner as the second cam member 62 except that the second cam member 200 does not have a reinforcing portion, and includes a friction portion 201 having a friction surface 201a and a cam surface 202a on which the cam follower 63 rolls. The part 202 is integrally formed. In FIG. 4, the contour of the cross-sectional shape when the cam mechanism of the second cam member 62 and the second cam member 200 is not operated is indicated by a two-dot chain line, and the contour of the cross-sectional shape when the cam mechanism is operated is indicated by a solid line. In this figure, the deformation amounts of the second cam member 62 and the second cam member 200 are exaggerated for the sake of explanation.

図４（ｂ）に示すように、第２カム部材２００のカム面２０２ａがカムフォロア６３からカム力を受けると第２カム部材２００が弾性変形し、変形前の状態に比較して、カム部２０２はリヤハウジング２２側に、摩擦部２０１は、特にその外周部において、リヤハウジング２２側とは反対側に変位する。この結果、カム力が摩擦面２０１ａの内周側に集中してしまう。   As shown in FIG. 4B, when the cam surface 202a of the second cam member 200 receives a cam force from the cam follower 63, the second cam member 200 is elastically deformed, and the cam portion 202 is compared with the state before the deformation. Is displaced to the rear housing 22 side, and the frictional portion 201 is displaced to the side opposite to the rear housing 22 side, particularly at the outer periphery thereof. As a result, the cam force is concentrated on the inner peripheral side of the friction surface 201a.

一方、図４（ａ）に示すように、第２カム部材６２は補強部６２３を備えているため、カム機構６の作動時の変形量が、例えば第２カム部材２００の半分以下に抑えられている。このため、第２カム部材２００に比較して、第２カム部材６２をリヤハウジング２２に押し付ける力の摩擦面６２１ａの内周側への集中が緩和され、第２カム部材２００よりもカム力が均等に摩擦面６２１ａに作用する。   On the other hand, as shown in FIG. 4A, since the second cam member 62 includes the reinforcing portion 623, the deformation amount when the cam mechanism 6 is operated is suppressed to, for example, less than half of that of the second cam member 200. ing. Therefore, as compared with the second cam member 200, the concentration of the force pressing the second cam member 62 against the rear housing 22 on the inner peripheral side of the friction surface 621a is alleviated, and the cam force is greater than that of the second cam member 200. It acts on the friction surface 621a evenly.

（第１の実施の形態の効果）
以上説明した本発明の第１の実施の形態によれば、次に示す効果が得られる。 (Effects of the first embodiment)
According to the first embodiment of the present invention described above, the following effects can be obtained.

（１）補強部６２３を設けたことによりカム機構６の作動時における第２カム部材６２の変形が抑えられるので、補強部６２３を有しない場合に比較して、カム力が摩擦面６２１ａの全体に均等に作用する。その結果、ハウジング２とインナシャフト３との差動回転時において、第２カム部材６２に発生する摩擦トルクが大きくなり、駆動力伝達装置１を小型に構成しても、必要なトルク伝達容量を確保できる。 (1) Since the deformation of the second cam member 62 during operation of the cam mechanism 6 is suppressed by providing the reinforcing portion 623, the cam force is generated on the entire friction surface 621a as compared with the case where the reinforcing portion 623 is not provided. Works equally well. As a result, at the time of differential rotation between the housing 2 and the inner shaft 3, the friction torque generated in the second cam member 62 increases, and the required torque transmission capacity can be obtained even if the driving force transmission device 1 is made compact. It can be secured.

（２）補強部６２３は、第２カム部材６２の側面６２ａの周方向の全体ではなく、その一部に形成されているため、例えば第２カム部材の全体を厚く形成した場合に比較して、第２カム部材６２を軽量化することができ、カム機構６の動作レスポンスを向上できる。 (2) Since the reinforcing portion 623 is formed not in the entire circumferential direction of the side surface 62a of the second cam member 62 but in a part thereof, for example, compared with a case where the entire second cam member is formed thick. The second cam member 62 can be reduced in weight, and the operation response of the cam mechanism 6 can be improved.

（３）第２カム部材６２は、補強部６２３の内周側の端部６２３ａが第２カム面６２２ａの径方向の中心位置６２２ｃよりも内周側に位置し、外周側の端部６２３ｂが摩擦面６２１ａの内周円６２１ｂよりも外周側に位置するように構成されているので、補強部６２３を介してカム力をカム部６２２から摩擦部６２１に伝達することができる。 (3) As for the 2nd cam member 62, the edge part 623a of the inner peripheral side of the reinforcement part 623 is located in the inner peripheral side rather than the center position 622c of the radial direction of the 2nd cam surface 622a, and the edge part 623b of the outer peripheral side is located. Since the friction surface 621 a is configured to be positioned on the outer peripheral side of the inner peripheral circle 621 b, the cam force can be transmitted from the cam portion 622 to the friction portion 621 via the reinforcing portion 623.

（４）補強部６２３は第２カム部材６２と一体に設けられているので、例えば素材のプレス成型により、第２カム部材６２のカム部６２２及び摩擦部６２１の形成と同時に補強部６２３を形成することができる。 (4) Since the reinforcing portion 623 is provided integrally with the second cam member 62, the reinforcing portion 623 is formed simultaneously with the formation of the cam portion 622 and the friction portion 621 of the second cam member 62, for example, by press molding of the material. can do.

［第２の実施の形態］
図５は、本発明の第２の実施の形態に係るカム機構８を備えた電磁クラッチ１１及びその周辺部の概略構成を示す全体図である。この電磁クラッチ１１は、円筒状の回転部材８０を非回転部材であるケーシング９に対して回り止めするためのブレーキ装置として機能し、例えば遊星歯車機構によるトルク伝達の経路を切り替えるため等に用いられる。 [Second Embodiment]
FIG. 5 is an overall view showing a schematic configuration of the electromagnetic clutch 11 including the cam mechanism 8 according to the second embodiment of the present invention and its peripheral portion. The electromagnetic clutch 11 functions as a brake device for preventing the cylindrical rotating member 80 from rotating with respect to the casing 9 that is a non-rotating member, and is used, for example, to switch a torque transmission path by a planetary gear mechanism. .

電磁クラッチ１１は、回転部材８０と、回転部材８０の鍔部８２に形成されたカム面８２ａを転動する球状のカムフォロア８３と、カム面８２ａに対向する面にカム面８４１ａが形成された板状のカム部材８４と、カム部材８４を軸方向移動させる磁力を発生する電磁コイル７１と、電磁コイル７１を保持する磁性材料からなるヨーク７２とを備えて構成されている。回転部材８０は本発明の第１カム部材の一例であり、カム部材８４は本発明の第２カム部材の一例である。   The electromagnetic clutch 11 includes a rotating member 80, a spherical cam follower 83 that rolls on a cam surface 82a formed on the flange 82 of the rotating member 80, and a plate in which a cam surface 841a is formed on a surface facing the cam surface 82a. And a yoke 72 made of a magnetic material that holds the electromagnetic coil 71. The electromagnetic coil 71 generates a magnetic force that moves the cam member 84 in the axial direction. The rotating member 80 is an example of the first cam member of the present invention, and the cam member 84 is an example of the second cam member of the present invention.

（回転部材８０の構成）
回転部材８０は、内面にシャフト（図示せず）が挿通される貫通孔が形成された円筒部８１と、円筒部８１の軸方向の一端から径方向外側に突出して形成された環状の鍔部８２とが一体に形成されている。円筒部８１の内周面の軸方向一側には、シャフトと回転部材８０との相対回転を規制するための、回転軸Ｏ_２に沿って形成されたストレートスプライン嵌合部８１ａが設けられている。ストレートスプライン嵌合部８１ａの外側にあたる円筒部８１の外周面には、ボール軸受７５の内輪７５１が嵌合されている。 (Configuration of Rotating Member 80)
The rotating member 80 includes a cylindrical portion 81 in which a through-hole through which a shaft (not shown) is inserted is formed on the inner surface, and an annular flange portion that protrudes radially outward from one axial end of the cylindrical portion 81. 82 is integrally formed. A straight spline fitting portion 81 a formed along the rotation axis O ₂ for restricting relative rotation between the shaft and the rotation member 80 is provided on one side in the axial direction of the inner peripheral surface of the cylindrical portion 81. Yes. An inner ring 751 of a ball bearing 75 is fitted to the outer peripheral surface of the cylindrical portion 81 that is outside the straight spline fitting portion 81a.

鍔部８２の軸方向の一方（ストレートスプライン嵌合部８１ａが形成された側）の側面に形成されたカム面８２ａは、回転部材８０の周方向に延び、その中央部における軸方向の深さが最も深く、周方向の端部に向かうにつれて浅くなるように形成されている。   A cam surface 82a formed on one side surface of the flange portion 82 in the axial direction (the side on which the straight spline fitting portion 81a is formed) extends in the circumferential direction of the rotating member 80 and has an axial depth at the central portion thereof. Is deepest and becomes shallower toward the end in the circumferential direction.

（カム部材８４の構成）
カム部材８４は、中心部に回転部材８０が挿通される挿通孔８４ａが形成された炭素鋼等の金属材料からなる環状の部材であり、回転部材８０の円筒部８１に外嵌されている。カム部材８４は、カム面８４１ａが形成されたカム部８４１、及びカム部８４１の外周側に設けられた摩擦部８４２とからなる本体部８４０と、本体部８４０の鍔部８２に面した側面に形成された補強部８４３とが一体に形成されている。補強部８４３の詳細については後述する。 (Configuration of cam member 84)
The cam member 84 is an annular member made of a metal material such as carbon steel in which an insertion hole 84 a through which the rotation member 80 is inserted is formed at the center, and is externally fitted to the cylindrical portion 81 of the rotation member 80. The cam member 84 has a body portion 840 including a cam portion 841 formed with a cam surface 841 a and a friction portion 842 provided on the outer peripheral side of the cam portion 841, and a side surface facing the flange portion 82 of the body portion 840. The formed reinforcing portion 843 is integrally formed. Details of the reinforcing portion 843 will be described later.

カム部８４１のカム面８４１ａは、カム部材８４の周方向に延び、その中央部における軸方向の深さが最も深く、周方向の端部に向かうにつれて浅くなるように形成されている。   The cam surface 841a of the cam portion 841 extends in the circumferential direction of the cam member 84, and is formed so that the axial depth at the center portion is the deepest and becomes shallower toward the end portion in the circumferential direction.

摩擦部８４２の軸方向一側の側面（補強部８４３とは反対側の側面）には、後述するヨーク７２の内周側摩擦面７２ａ及び外周側摩擦面７２ｂとそれぞれ摩擦係合する内周側摩擦面８４２ａ及び外周側摩擦面８４２ｂが形成されている。   An inner peripheral side that frictionally engages an inner peripheral friction surface 72a and an outer peripheral friction surface 72b of a yoke 72, which will be described later, on a side surface on the one axial side of the friction portion 842 (a side surface opposite to the reinforcing portion 843). A friction surface 842a and an outer peripheral friction surface 842b are formed.

また、カム部材８４は、皿バネ７３によって鍔部８２側に付勢されている。皿バネ７３は、ボール軸受７５の内輪７５１との間に配置されたスペーサ７４により軸方向移動が規制されている。   Further, the cam member 84 is urged toward the flange portion 82 by the disc spring 73. The disc spring 73 is restricted from moving in the axial direction by a spacer 74 disposed between the disc bearing 73 and the inner ring 751 of the ball bearing 75.

回転部材８０の鍔部８２には、カム面８２ａが周方向の複数の箇所に形成され、カム部材８４のカム部８４１にも同数のカム面８４１ａが形成されている。カムフォロア８３は、各カム面８２ａとそれに対応するカム面８４１ａとの間に介在している。カム部材８４は、カム面８４１ａ及び回転部材８０のカム面８２ａをカムフォロア８３が転動する範囲において、回転部材８０との相対回転が可能である。   Cam surfaces 82 a are formed at a plurality of locations in the circumferential direction on the flange portion 82 of the rotating member 80, and the same number of cam surfaces 841 a are formed on the cam portions 841 of the cam member 84. The cam follower 83 is interposed between each cam surface 82a and the corresponding cam surface 841a. The cam member 84 can rotate relative to the rotating member 80 in a range where the cam follower 83 rolls on the cam surface 841a and the cam surface 82a of the rotating member 80.

（ヨーク７２の構成）
ヨーク７２は、炭素鋼等の磁性材料からなり、カム部材８４の軸方向に対向して配置され、ボルト９１によってケーシング９に相対回転不能かつ軸方向移動不能に固定されている。ヨーク７２には、軸方向のカム部材８４側に開口した断面コの字状の環状凹部７２０が形成され、環状凹部７２０に電磁コイル７１が保持されている。環状凹部７２０の内周側におけるカム部材８４との対向面に環状の内周側摩擦面７２ａが形成され、環状凹部７２０の外周側におけるカム部材８４との対向面に環状の外周側摩擦面７２ｂが形成されている。 (Configuration of yoke 72)
The yoke 72 is made of a magnetic material such as carbon steel, is disposed so as to face the cam member 84 in the axial direction, and is fixed to the casing 9 by a bolt 91 so as not to be relatively rotatable and axially movable. The yoke 72 is formed with an annular recess 720 having a U-shaped cross section that is open toward the cam member 84 in the axial direction, and the electromagnetic coil 71 is held in the annular recess 720. An annular inner peripheral friction surface 72a is formed on the inner surface of the annular recess 720 facing the cam member 84, and an annular outer friction surface 72b is formed on the outer surface of the annular recess 720 facing the cam member 84. Is formed.

ヨーク７２の内周面には、ボール軸受７５の外輪７５２が嵌合されており、ヨーク７２は、回転部材８０を回転可能に支持している。なお、ボール軸受７５は、回転部材８０の円筒部８１の外周面に設けられた段差部８１ｂとスナップリング７５３により内輪７５１の軸方向の位置が固定され、ヨーク７２の内周面に設けられた段差部７２ｃとスナップリング７５４により外輪７５２の軸方向の位置が固定されている。   An outer ring 752 of a ball bearing 75 is fitted to the inner peripheral surface of the yoke 72, and the yoke 72 supports the rotating member 80 in a rotatable manner. The ball bearing 75 is provided on the inner peripheral surface of the yoke 72, with the axial position of the inner ring 751 fixed by a step portion 81 b provided on the outer peripheral surface of the cylindrical portion 81 of the rotating member 80 and the snap ring 753. The position of the outer ring 752 in the axial direction is fixed by the stepped portion 72c and the snap ring 754.

電磁コイル７１は、ヨーク７２の環状凹部７２０に保持され、スナップリング７２１によって抜け止めされている。電磁コイル７１には、図略の電線によって電流が供給される。   The electromagnetic coil 71 is held in the annular recess 720 of the yoke 72 and is prevented from coming off by a snap ring 721. A current is supplied to the electromagnetic coil 71 by an unillustrated electric wire.

（補強部８４３の構成）
図６は、カム部材８４の補強部８４３が設けられた側の側面を示す。この図では、内周側摩擦面８４２ａの内周円８４２ｃ及び外周円８４２ｄと、外周側摩擦面８４２ｂの内周円８４２ｅを破線で示している。 (Configuration of reinforcing portion 843)
FIG. 6 shows a side surface of the cam member 84 on the side where the reinforcing portion 843 is provided. In this figure, the inner circumference circle 842c and the outer circumference circle 842d of the inner circumference side friction surface 842a and the inner circumference circle 842e of the outer circumference side friction surface 842b are indicated by broken lines.

カム部材８４のカム部８４１には、６つのカム面８４１ａが等間隔に配置されている。各カム面８４１ａは、カム部材８４の周方向に沿って湾曲する円弧状に形成されている。周方向に隣り合う２つのカム面８４１ａの間には、カム面が形成されていない非形成領域８４１ｂ（図６に二点鎖線で一箇所のみ示す）が設けられている。   Six cam surfaces 841a are arranged at equal intervals on the cam portion 841 of the cam member 84. Each cam surface 841 a is formed in an arc shape that curves along the circumferential direction of the cam member 84. Between the two cam surfaces 841a adjacent to each other in the circumferential direction, a non-formation region 841b (only one location is indicated by a two-dot chain line in FIG. 6) where no cam surface is formed is provided.

カム部材８４には、内周側から外周側に向かって延在する、カム面８４１ａと同数（６つ）の補強部８４３が設けられている。補強部８４３は、補強部８４３が設けられていない領域８４ｂよりもカム部材８４の軸方向の厚みを厚く形成することにより、カム部材８４と一体に設けられている。   The cam member 84 is provided with the same number (six) of reinforcing portions 843 as the cam surface 841a extending from the inner peripheral side toward the outer peripheral side. The reinforcing portion 843 is provided integrally with the cam member 84 by forming the cam member 84 thicker in the axial direction than the region 84b where the reinforcing portion 843 is not provided.

補強部８４３は、非形成領域８４１ｂを含む領域に設けられ、補強部８４３の内周側の端部８４３ａは、カム面８４１ａの径方向の中心位置８４１ｃよりも内周側に位置し、挿通孔８４ａの内周面に達している。また、補強部８４３の外周側の端部８４３ｂは、外周側摩擦面８４２ｂの内周円８４２ｅよりも外周側に位置している。このように、補強部８４３は、内周側摩擦面８４２ａ及び外周側摩擦面８４２ｂの軸方向反対側にあたる範囲に形成されている。   The reinforcing portion 843 is provided in a region including the non-forming region 841b, and an end portion 843a on the inner peripheral side of the reinforcing portion 843 is located on the inner peripheral side with respect to the center position 841c in the radial direction of the cam surface 841a. It reaches the inner peripheral surface of 84a. Further, the outer end 843b of the reinforcing portion 843 is located on the outer peripheral side with respect to the inner peripheral circle 842e of the outer peripheral friction surface 842b. Thus, the reinforcement part 843 is formed in the range which hits the axial direction opposite side of the inner peripheral side friction surface 842a and the outer peripheral side friction surface 842b.

（電磁クラッチ１１の動作）
電磁コイル７１に通電されると、図５に破線で示すように、ヨーク７２及びカム部材８４により形成される磁路に磁束Ｍ_２が発生し、カム部材８４がヨーク７２の側に引き寄せられ、カム部材８４の内周側摩擦面８４２ａがヨーク７２の内周側摩擦面７２ａに、カム部材８４の外周側摩擦面８４２ｂがヨーク７２の外周側摩擦面７２ｂに、それぞれ摩擦接触する。 (Operation of electromagnetic clutch 11)
When energizing of solenoid coil 71, as indicated by a broken line in FIG. 5, the magnetic flux M ₂ is generated in the magnetic path formed by the yoke 72 and the cam member 84, the cam member 84 are attracted to the side of the yoke 72, The inner peripheral friction surface 842a of the cam member 84 is in frictional contact with the inner peripheral friction surface 72a of the yoke 72, and the outer peripheral friction surface 842b of the cam member 84 is in frictional contact with the outer peripheral friction surface 72b of the yoke 72.

この状態で回転部材８０が回転すると、カムフォロア８３がカム面８２ａ及びカム面８４１ａを転動し、回転部材８０の鍔部８２に対してカム部材８４を軸方向に離間させるカム力が発生する。このカム力により、カム部材８４がヨーク７２に向かって押圧され、内周側摩擦面８４２ａと内周側摩擦面７２ａ、及び外周側摩擦面８４２ｂと外周側摩擦面７２ｂの摩擦力が増大し、カム部材８４とヨーク７２が摩擦係合する。これにより、回転部材８０がケーシング９に対して回り止めされる。   When the rotating member 80 rotates in this state, the cam follower 83 rolls on the cam surface 82a and the cam surface 841a, and a cam force that separates the cam member 84 in the axial direction from the flange portion 82 of the rotating member 80 is generated. With this cam force, the cam member 84 is pressed toward the yoke 72, and the frictional forces of the inner peripheral friction surface 842a and the inner peripheral friction surface 72a, and the outer peripheral friction surface 842b and the outer peripheral friction surface 72b increase. The cam member 84 and the yoke 72 are frictionally engaged. Thereby, the rotation member 80 is prevented from rotating with respect to the casing 9.

一方、電磁コイル７１への通電が遮断されると、皿バネ７３の付勢力によってカム部材８４がヨーク７２から離間し、カム部材８４とヨーク７２との摩擦係合が解除される。すると、カムフォロア８３がカム面８４１ａ及びカム面８２ａの最も深い部位（中立位置）に移動し、カム力が消滅する。これにより、回転部材８０は、カムフォロア８３，カム部材８４，及び皿バネ７３と共に回転可能となる。   On the other hand, when the energization of the electromagnetic coil 71 is interrupted, the cam member 84 is separated from the yoke 72 by the biasing force of the disc spring 73, and the frictional engagement between the cam member 84 and the yoke 72 is released. Then, the cam follower 83 moves to the deepest part (neutral position) of the cam surface 841a and the cam surface 82a, and the cam force disappears. As a result, the rotating member 80 can rotate together with the cam follower 83, the cam member 84, and the disc spring 73.

（第２の実施の形態の効果）
以上説明した本発明の第２の実施の形態によれば、第１の実施の形態の効果と同様の効果に加え、カム部材８４がヨーク７２に直接摩擦係合するので、少ない部品数で電磁クラッチ１１を構成できる。 (Effect of the second embodiment)
According to the second embodiment of the present invention described above, since the cam member 84 is directly frictionally engaged with the yoke 72 in addition to the same effect as the first embodiment, the electromagnetic force can be reduced with a small number of parts. The clutch 11 can be configured.

［第３の実施の形態］
図７は、本発明の第３の実施の形態に係る電磁クラッチ１１のカム部材８４Ａを示す。本実施の形態に係る電磁クラッチ１１は、第２の実施の形態と比べてカム部材８４がカム部材８４Ａに置換された他は同一の構成であるので、全体図の図示を省略する。また、カム部材８４Ａは、補強部８５の構造がカム部材８４の補強部８４３とは異なるが、その他は同一であるので、同一の構成要素には同一の符号を付して説明を省略する。 [Third Embodiment]
FIG. 7 shows a cam member 84A of the electromagnetic clutch 11 according to the third embodiment of the present invention. The electromagnetic clutch 11 according to the present embodiment has the same configuration as that of the second embodiment except that the cam member 84 is replaced with the cam member 84A. The cam member 84A is different in the structure of the reinforcing portion 85 from the reinforcing portion 843 of the cam member 84, but is otherwise the same. Therefore, the same components are denoted by the same reference numerals and description thereof is omitted.

カム部材８４Ａに設けられた補強部８５は、カム部材８４Ａの周方向に沿って環状に形成された環状補強部８５１と、環状補強部８５１の外周側の端部８５１ａから外周側に延びるように形成されたスポーク状補強部８５２とを有している。補強部８５は、補強部８５が設けられていない領域８５ｂよりもカム部材８４Ａの軸方向の厚みを厚く形成することにより、カム部材８４Ａと一体に設けられている。   The reinforcing portion 85 provided on the cam member 84A extends from the annular reinforcing portion 851 formed in an annular shape along the circumferential direction of the cam member 84A and the outer end 851a of the annular reinforcing portion 851 to the outer peripheral side. And a spoke-shaped reinforcing portion 852 formed. The reinforcing portion 85 is provided integrally with the cam member 84A by forming the cam member 84A thicker in the axial direction than the region 85b where the reinforcing portion 85 is not provided.

環状補強部８５１は、カム面８４１ａを含む領域に形成され、その一部は内周側摩擦面８４２ａの軸方向反対側にあたる範囲に形成されている。   The annular reinforcing portion 851 is formed in a region including the cam surface 841a, and a part of the annular reinforcing portion 851 is formed in a range corresponding to the axially opposite side of the inner peripheral friction surface 842a.

スポーク状補強部８５２は、環状補強部８５１の外周側の端部８５１ａから放射状に形成され、その外周側の端部８５２ａは外周側摩擦面８４２ｂの内周円８４２ｅよりも外周側に位置している。また、スポーク状補強部８５２は、隣り合うカム面８４１ａの間の位置に対応する外周側に、カム面８４１ａと同数（６つ）設けられている。   The spoke-like reinforcing portion 852 is formed radially from the outer peripheral end 851a of the annular reinforcing portion 851, and the outer peripheral end 852a is located on the outer peripheral side of the inner peripheral circle 842e of the outer peripheral friction surface 842b. Yes. Further, the same number (six) of the spoke-shaped reinforcing portions 852 as the cam surfaces 841a are provided on the outer peripheral side corresponding to the position between the adjacent cam surfaces 841a.

本実施の形態によれば、上記の第２の実施の形態の効果と同様の効果がある。また、カム面８４１ａがカムフォロア８３から受けるカム力が環状補強部８５１によって周方向に分散されるので、カムフォロア８３が存在する位置の裏側にあたる内周側摩擦面８４２ａの周辺にカム力が集中してしまうことが抑制され、カム力が環状補強部８５１を介してより的確にスポーク状補強部８５２に伝達される。従って、より確実にカム部材８４Ａの変形が抑制される。   According to the present embodiment, there are the same effects as the effects of the second embodiment. Further, since the cam force received by the cam surface 841a from the cam follower 83 is dispersed in the circumferential direction by the annular reinforcing portion 851, the cam force is concentrated around the inner peripheral friction surface 842a, which is the back side of the position where the cam follower 83 exists. The cam force is more accurately transmitted to the spoke-like reinforcing portion 852 via the annular reinforcing portion 851. Therefore, the deformation of the cam member 84A is more reliably suppressed.

［他の実施の形態］
以上、本発明のカム機構及び電磁クラッチを上記の実施の形態に基づいて説明したが、本発明は上記の実施の形態に限定されるものではなく、その要旨を逸脱しない範囲で種々の態様において実施することが可能であり、例えば次に示すような変形も可能である。 [Other embodiments]
As mentioned above, although the cam mechanism and electromagnetic clutch of the present invention have been described based on the above-described embodiment, the present invention is not limited to the above-described embodiment, and can be variously modified without departing from the scope of the present invention. For example, the following modifications are possible.

（１）第１及び第２の実施の形態における補強部、及び第３の実施の形態におけるスポーク状補強部は、径方向に沿って一定の幅で設けられているが、径方向に対して傾斜して設けてもよい。また、補強部又はスポーク状補強部の幅寸法は一定でなくともよく、例えばカム面の内周側又は外周側、若しくは内周側及び外周側に向かって周方向の幅が広くなるように形成してもよい。また、補強部の厚みも一定に限らない。 (1) The reinforcing portions in the first and second embodiments and the spoke-like reinforcing portions in the third embodiment are provided with a constant width along the radial direction, but with respect to the radial direction. You may provide inclining. In addition, the width dimension of the reinforcing part or the spoke-like reinforcing part may not be constant, for example, it is formed so that the width in the circumferential direction becomes wider toward the inner peripheral side or outer peripheral side of the cam surface, or toward the inner peripheral side and the outer peripheral side. May be. Further, the thickness of the reinforcing portion is not limited to a constant value.

（２）上記各実施の形態では、電磁コイルへの通電時にカム部材がリヤハウジング又はヨークに摩擦係合し、非通電時には皿バネの付勢力によって摩擦係合が解除されるように構成したが、これとは逆に、電磁コイルへの非通電時に皿バネ等の弾性部材の付勢力によってカム部材が他の部材に摩擦係合し、電磁コイルへの通電時に磁力によって摩擦係合が解除されるように構成してもよい。 (2) In each of the above embodiments, the cam member is frictionally engaged with the rear housing or the yoke when the electromagnetic coil is energized, and the frictional engagement is released by the biasing force of the disc spring when deenergized. On the contrary, the cam member is frictionally engaged with other members by the biasing force of an elastic member such as a disc spring when the electromagnetic coil is not energized, and the frictional engagement is released by the magnetic force when the electromagnetic coil is energized. You may comprise.

（３）カム機構及び電磁クラッチの用途及び適用対象についても特に制限はない。 (3) There are no particular restrictions on the use and application object of the cam mechanism and electromagnetic clutch.

１…駆動力伝達装置、２…ハウジング、３…インナシャフト、３ａ…端面、３ｂ…中空部、３ｃ…ストレートスプライン嵌合部、３ｄ…端面、３ｅ…中空部、３ｆ…壁部、３ｇ…ストレートスプライン嵌合部、３ｈ…段差部、４…メインクラッチ、５…電磁コイル、５ａ…電線、６…カム機構、８…カム機構、９…ケーシング、９ａ…凹部、１０，１１…電磁クラッチ、２１…フロントハウジング、２１ａ…収容空間、２１ｂ…ストレートスプライン嵌合部、２２…リヤハウジング、２２ａ…収容空間、２２ｂ…摩擦面、４１…アウタクラッチプレート、４１ａ…スプライン嵌合部、４２…インナクラッチプレート、４２ａ…スプライン嵌合部、４２ｂ…孔、５１…ヨーク、５１ａ，５１ｂ…エアギャップ、５１ｃ…収容空間、５１ｄ…孔、５２…シール軸受、６１…第１カム部材、６２…第２カム部材、６２ａ…側面、６２ｂ…領域、６２ｃ…挿通孔、６３…カムフォロア、６４，６５…皿バネ、６６…スナップリング、７１…電磁コイル、７２ａ…内周側摩擦面、７２ｂ…外周側摩擦面、７２ｃ…段差部、７３，７６…皿バネ、７４…スペーサ、７５…ボール軸受、８０…回転部材、８１…円筒部、８１ａ…ストレートスプライン嵌合部、８１ｂ…段差部、８２…鍔部、８２ａ…カム面、８３…カムフォロア、８４，８４Ａ…カム部材、８４ａ…挿通孔、８４ｂ…領域、８５…補強部、８５ｂ…領域、９１…ボルト、１０１…４輪駆動車、１０２…エンジン、１０３…トランスアクスル、１０４…フロントアクスルシャフト、１０５…前輪、１０６…プロペラシャフト、１０７…ディファレンシャルキャリア、１０８…ドライブピニオンシャフト、１０９…リヤディファレンシャル、１１０…リヤアクスルシャフト、１１１…後輪、１１２…コントローラ、２００…カム部材、２０１…摩擦部、２０１ａ…摩擦面、２０２…カム部、２０２ａ…カム面、２１０…ボール軸受、２２０…ニードル軸受、２２１…外側部材、２２２…中間部材、２２３…内側部材、６１１…押圧部、６１１ａ…押圧面、６１１ｂ…ストレートスプライン嵌合部、６１２…カム部、６１２ａ…第１カム面、６２０…本体部、６２１…摩擦部、６２１ａ…摩擦面、６２１ｂ…内周円、６２２…カム部、６２２ａ…第２カム面、６２２ｂ…非形成領域、６２２ｃ…中心位置、６２３…補強部、６２３ａ，６２３ｂ…端部、７２０…環状凹部、７２１，７５３，７５４…スナップリング、７５１…内輪、７５２…外輪、８４０…本体部、８４１…カム部、８４１ａ…カム面、８４１ｂ…非形成領域、８４１ｃ…中心位置、８４２…摩擦部８４２ａ…内周側摩擦面、８４２ｂ…外周側摩擦面、８４２ｃ，８４２ｅ…内周円、８４２ｄ…外周円、８４３…補強部、８４３ａ，８４３ｂ…端部、８５１…環状補強部、８５１ａ，８５２ａ…端部、８５２…スポーク状補強部、Ｍ，Ｍ_２…磁束、Ｏ，Ｏ_２…回転軸 DESCRIPTION OF SYMBOLS 1 ... Driving force transmission device, 2 ... Housing, 3 ... Inner shaft, 3a ... End surface, 3b ... Hollow part, 3c ... Straight spline fitting part, 3d ... End surface, 3e ... Hollow part, 3f ... Wall part, 3g ... Straight Spline fitting portion, 3h ... step portion, 4 ... main clutch, 5 ... electromagnetic coil, 5a ... electric wire, 6 ... cam mechanism, 8 ... cam mechanism, 9 ... casing, 9a ... recess, 10,11 ... electromagnetic clutch, 21 ... Front housing, 21a ... Housing space, 21b ... Straight spline fitting part, 22 ... Rear housing, 22a ... Housing space, 22b ... Friction surface, 41 ... Outer clutch plate, 41a ... Spline fitting part, 42 ... Inner clutch plate 42a ... spline fitting part, 42b ... hole, 51 ... yoke, 51a, 51b ... air gap, 51c ... accommodation space, 51d ... hole, 2 ... Seal bearing, 61 ... 1st cam member, 62 ... 2nd cam member, 62a ... Side surface, 62b ... Area | region, 62c ... Insertion hole, 63 ... Cam follower, 64, 65 ... Disc spring, 66 ... Snap ring, 71 ... Electromagnetic coil, 72a ... inner friction surface, 72b ... outer friction surface, 72c ... stepped portion, 73, 76 ... disc spring, 74 ... spacer, 75 ... ball bearing, 80 ... rotating member, 81 ... cylindrical portion, 81a ... straight spline fitting part, 81b ... step part, 82 ... collar part, 82a ... cam surface, 83 ... cam follower, 84, 84A ... cam member, 84a ... insertion hole, 84b ... area, 85 ... reinforcing part, 85b ... area , 91 ... Bolt, 101 ... Four-wheel drive vehicle, 102 ... Engine, 103 ... Transaxle, 104 ... Front axle shaft, 105 ... Front wheel, 106 ... Propeller shaft, 107 Differential carrier 108 ... Drive pinion shaft 109 ... Rear differential 110 ... Rear axle shaft 111 ... Rear wheel 112 ... Controller 200 ... Cam member 201 ... Friction part 201a ... Friction surface 202 ... Cam part 202a ... Cam surface, 210 ... ball bearing, 220 ... needle bearing, 221 ... outer member, 222 ... intermediate member, 223 ... inner member, 611 ... pressing portion, 611a ... pressing surface, 611b ... straight spline fitting portion, 612 ... cam portion , 612a ... first cam surface, 620 ... main body portion, 621 ... friction portion, 621a ... friction surface, 621b ... inner circle, 622 ... cam portion, 622a ... second cam surface, 622b ... non-forming region, 622c ... center Position, 623 ... reinforcing part, 623a, 623b ... end, 720 ... annular recess, 721 , 753,754 ... Snap ring, 751 ... Inner ring, 752 ... Outer ring, 840 ... Main body part, 841 ... Cam part, 841a ... Cam surface, 841b ... Non-formation region, 841c ... Center position, 842 ... Friction part 842a ... Inner circumference Side friction surface, 842b ... outer peripheral side friction surface, 842c, 842e ... inner circumference circle, 842d ... outer circumference circle, 843 ... reinforcement part, 843a, 843b ... end part, 851 ... annular reinforcement part, 851a, 852a ... end part, 852 ... Spoke-shaped reinforcing part, M, M ₂ ... Magnetic flux, O, O ₂ ... Rotary shaft

Claims (4)

周方向に延びるように形成された第１カム面を有する第１カム部材と、
前記第１カム部材との相対回転により軸方向のカム力を発生させる第２カム面が形成された本体部、及び前記第２カム面の内周側と外周側とに亘って径方向に延びるように前記本体部と一体に形成され、前記カム力による前記本体部の変形を抑制する補強部を有する第２カム部材と、
を備えたカム機構。 A first cam member having a first cam surface formed to extend in the circumferential direction;
A main body portion formed with a second cam surface that generates an axial cam force by relative rotation with the first cam member, and extends radially across an inner peripheral side and an outer peripheral side of the second cam surface. A second cam member formed integrally with the main body portion and having a reinforcing portion that suppresses deformation of the main body portion due to the cam force;
Cam mechanism with 前記第２カム部材は、前記カム面が形成された側面の軸方向反対側の側面に、前記カム力により摩擦相手部材と摩擦係合する摩擦面を有し、
前記補強部は、少なくとも一部が前記摩擦面に対応する径方向の範囲に形成されている請求項１に記載のカム機構。 The second cam member has a friction surface that frictionally engages with a friction counterpart member by the cam force on a side surface opposite to the axial direction of the side surface on which the cam surface is formed,
The cam mechanism according to claim 1, wherein at least a part of the reinforcing portion is formed in a radial range corresponding to the friction surface. 前記第２カム部材は、前記本体部に複数の前記第２カム面を有し、前記補強部は、周方向に隣り合う前記第２カム面の間のそれぞれの位置に対応して形成されている請求項１又は２に記載のカム機構。   The second cam member has a plurality of the second cam surfaces on the main body, and the reinforcing portion is formed corresponding to each position between the second cam surfaces adjacent in the circumferential direction. The cam mechanism according to claim 1 or 2. 周方向に延びるように形成された第１カム面を有する第１カム部材と、
前記第１カム部材との相対回転により軸方向のカム力を発生させる第２カム面、及び前記カム力により摩擦相手部材と摩擦係合する摩擦面が形成された本体部を有する第２カム部材と、
前記第２カム部材の前記摩擦面を前記摩擦相手部材に接触させるように前記第２カム部材を軸方向移動させる磁力を発生する電磁コイルと、を備え、
前記第２カム部材は、前記第２カム面の内周側と外周側とに亘って径方向に延びるように前記本体部と一体に形成され、前記カム力による前記本体部の変形を抑制する補強部を有する電磁クラッチ。 A first cam member having a first cam surface formed to extend in the circumferential direction;
A second cam member having a second cam surface that generates an axial cam force by relative rotation with the first cam member, and a main body portion formed with a friction surface that frictionally engages with a friction counterpart member by the cam force. When,
An electromagnetic coil that generates a magnetic force to move the second cam member in the axial direction so that the friction surface of the second cam member is brought into contact with the friction counterpart member,
The second cam member is formed integrally with the main body portion so as to extend in a radial direction across an inner peripheral side and an outer peripheral side of the second cam surface, and suppresses deformation of the main body portion due to the cam force. An electromagnetic clutch having a reinforcing portion.

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