JP2009209794A

JP2009209794A - Valve-timing adjusting device

Info

Publication number: JP2009209794A
Application number: JP2008053892A
Authority: JP
Inventors: Akiyuki Sudo; 彰之須藤; Taishi Morii; 泰詞森井
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2008-03-04
Filing date: 2008-03-04
Publication date: 2009-09-17
Anticipated expiration: 2028-03-04
Also published as: JP4900286B2

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve-timing adjusting device having high durability. <P>SOLUTION: A driving-side rotating element 10 and a driven-side rotating element 20 include wall parts 16, 21 for forming corners 72, 82 with internal gear parts 18, 22 located adjacent in the axial direction with respect to the internal gear parts 18, 22, respectively meshing with a planetary gear 50, and annular recessed parts 70, 80 of which closed ends 70b, 80b are positioned on an outer side, in the radial direction from gear bottom circles Cd, Cf of the internal gear parts 18, 22 on the opposite sides of opening ends 70a, 80a opening to the corners 72, 82, and which continue to the rotation directions of the internal gear parts 18, 22. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、内燃機関においてクランク軸からのトルク伝達によりカム軸が開閉する動弁のバルブタイミングを調整するバルブタイミング調整装置に関する。 The present invention relates to a valve timing adjusting device that adjusts the valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine.

従来、クランク軸と連動して回転する駆動側回転体及びカム軸と連動して回転する従動側回転体の間を遊星歯車機構により連繋させて、それら回転体間の相対位相（以下、「回転体間位相」という）に基づきバルブタイミングを調整するようにしたバルブタイミング調整装置が知られている。 Conventionally, a driving side rotating body that rotates in conjunction with a crankshaft and a driven side rotating body that rotates in conjunction with a camshaft are linked by a planetary gear mechanism, and the relative phase between these rotating bodies (hereinafter referred to as “rotation”). 2. Description of the Related Art A valve timing adjusting device that adjusts a valve timing on the basis of “inter-body phase” is known.

こうした装置の一種として特許文献１には、駆動側回転体及び従動側回転体に個別に設けた内歯車部を遊星歯車に噛合させて、遊星歯車の遊星運動により回転体間位相を変化させる、所謂差動歯車式の装置が開示されている。この装置は、コンパクトな設計で減速比を高めることができるので、設置スペースの制限を受け易い且つバルブタイミング調整に大きなトルクが必要な内燃機関のバルブタイミング調整装置として好適なものとなっている。 As a kind of such device, Patent Document 1 discloses that a planetary gear is meshed with an internal gear portion separately provided on a driving side rotating body and a driven side rotating body, and the phase between the rotating bodies is changed by planetary motion of the planetary gear. A so-called differential gear type device is disclosed. Since this device can increase the reduction ratio with a compact design, it is suitable as a valve timing adjusting device for an internal combustion engine that is easily limited in installation space and requires a large torque for valve timing adjustment.

さて、一般にバルブタイミング調整装置では、時々刻々と変化する内燃機関の運転状態にバルブタイミング調整を追従させるために作動頻度が高くなることから、特許文献１のような差動歯車式の装置の場合、各回転体の内歯車部と遊星歯車との噛合部分に磨耗が発生し易くなる。そこで、特許文献１の装置では、各回転体の内歯車部の内周側に潤滑液を供給して噛合界面の磨耗を軽減しつつ、磨耗紛等の異物を潤滑液と共に装置外部へ排出することにより、耐久性を高めている。
特開２００７−２３９６４２号公報 Now, in general, in the valve timing adjustment device, since the operation frequency becomes high in order to make the valve timing adjustment follow the operation state of the internal combustion engine which changes from moment to moment, in the case of the differential gear type device as in Patent Document 1 In addition, wear tends to occur at the meshing portion between the internal gear portion of each rotating body and the planetary gear. Therefore, in the apparatus of Patent Document 1, a lubricating liquid is supplied to the inner peripheral side of the internal gear portion of each rotating body to reduce wear on the meshing interface, and foreign matters such as wear powder are discharged together with the lubricating liquid to the outside of the apparatus. As a result, durability is improved.
JP 2007-239642 A

上述した特許文献１の装置において潤滑液を外部へ排出するための排出孔は、駆動側回転体において内歯車部に軸方向に隣接する壁部と当該内歯車部との間に形成される入隅に向かって開口するように、回転方向に間隔をあけて複数設けられている。しかし、内歯車部とその隣接壁部との間の入隅は、潤滑液の流れ方向が変化して潤滑液が淀み易い箇所となることから、潤滑液中の異物が入隅に滞留することが懸念され、しかも間隔をあけた各排出孔の開口端から回転方向に外れる箇所にて入隅に滞留している異物は、排出され難くなる。そのため、入隅に滞留する異物について各排出孔による排出作用を高めるには、潤滑液の供給量又は供給圧力を増大させる必要があるが、そうした供給諸元は、ポンプ等の供給源の性能に起因した制限を受けることになるため、十分な排出作用が得られずに耐久性が低下するおそれがある。 In the apparatus of Patent Document 1 described above, the discharge hole for discharging the lubricating liquid to the outside is an inlet formed between the wall portion adjacent to the internal gear portion in the axial direction and the internal gear portion in the drive side rotor. A plurality are provided at intervals in the rotational direction so as to open toward the corners. However, the entrance corner between the internal gear and the adjacent wall portion changes the flow direction of the lubricant and makes it easy for the lubricant to stagnate, so foreign matter in the lubricant will stay in the entrance corner. In addition, foreign matters staying in the corners at locations away from the opening ends of the respective discharge holes spaced apart from each other in the rotation direction are difficult to be discharged. For this reason, in order to increase the discharge action of each discharge hole for the foreign matter staying in the corner, it is necessary to increase the supply amount or supply pressure of the lubricating liquid, but such supply specifications are related to the performance of the supply source such as a pump. Since it is subject to the restriction caused by it, there is a risk that durability will be lowered without obtaining a sufficient discharging action.

本発明は、以上説明した問題に鑑みてなされたものであって、その目的は、高耐久性のバルブタイミング調整装置を提供することにある。 The present invention has been made in view of the problems described above, and an object thereof is to provide a highly durable valve timing adjusting device.

請求項１に記載の発明は、内燃機関においてクランク軸からのトルク伝達によりカム軸が開閉する動弁のバルブタイミングを調整するバルブタイミング調整装置であって、駆動側内歯車部を有し、クランク軸と連動して回転する駆動側回転体と、従動側内歯車部を有し、カム軸と連動して回転する従動側回転体と、駆動側内歯車部及び従動側内歯車部と噛合しつつ遊星運動することにより回転体間位相を変化させる遊星歯車と、を備え、駆動側内歯車部及び従動側内歯車部の内周側に潤滑液が供給源から供給されるバルブタイミング調整装置において、駆動側回転体及び従動側回転体の少なくとも一方である特定回転体は、駆動側内歯車部及び従動側内歯車部の少なくとも一方であって特定回転体に設けられる特定内歯車部に対し、軸方向に隣接して当該特定内歯車部との間に入隅を形成する壁部と、入隅に向かって開口する開口端とは反対側において閉塞される閉塞端が特定内歯車部の歯底よりも径方向の外側に位置すると共に、特定内歯車部の回転方向に連続する環状の凹部と、を有することを特徴とする。 According to a first aspect of the present invention, there is provided a valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine, comprising a drive-side internal gear portion, A drive-side rotating body that rotates in conjunction with the shaft and a driven-side internal gear portion, and a driven-side rotating body that rotates in conjunction with the camshaft, meshes with the driving-side internal gear portion and the driven-side internal gear portion. And a planetary gear that changes the phase between the rotating bodies by planetary motion while the lubricant is supplied from the supply source to the inner peripheral side of the driving-side internal gear portion and the driven-side internal gear portion. The specific rotating body that is at least one of the driving-side rotating body and the driven-side rotating body is at least one of the driving-side internal gear section and the driven-side internal gear section that is provided on the specific rotating body, Axially The wall portion that is in contact with the specific internal gear portion to form an entrance corner, and the closed end that is closed on the side opposite to the opening end that opens toward the entrance corner has a diameter that is larger than the root of the specific internal gear portion. And an annular recess that is located outside in the direction and is continuous in the rotation direction of the specific internal gear portion.

このような発明によると、特定回転体に設けられた特定内歯車部とその軸方向（以下、解決手段の欄では、この特定内歯車部の軸方向を「歯車軸方向」という）に隣接する壁部との間に形成される入隅には、特定内歯車部の回転方向（以下、解決手段の欄では、この特定内歯車部の回転方向を「歯車回転方向」という）に連続する環状の凹部が開口するので、特定内歯車部の内周側に供給された潤滑液中の異物は、入隅における歯車回転方向の任意箇所から凹部へ流入し得る。しかも、凹部において開口端と反対側にて閉塞される閉塞端は特定内歯車部の歯底よりも径方向の外側に位置するので、当該歯底が露出する入隅に到達した異物は、内燃機関運転中に特定回転体が回転して発生する遠心力の作用により、確実に開口端へ流入して閉塞端に向かって押し込まれることになる。以上によれば、潤滑液の流れ方向が変化する入隅に到達した異物について、歯車回転方向の到達位置に拘らず凹部へと流入させて捕捉することができる。したがって、潤滑液の供給源性能に起因した制限を受けることなく磨耗粉等の異物が潤滑液から除去されて、耐久性が高められることになるのである。 According to such an invention, the specific internal gear portion provided in the specific rotating body and its axial direction (hereinafter, in the column of solution means, the axial direction of the specific internal gear portion is referred to as “gear axis direction”). In the corner formed between the wall and the annular portion, there is an annular shape that continues in the direction of rotation of the specific internal gear portion (hereinafter, the direction of rotation of the specific internal gear portion is referred to as “gear rotation direction” in the column of solution). Therefore, the foreign matter in the lubricating liquid supplied to the inner peripheral side of the specific internal gear portion can flow into the concave portion from an arbitrary position in the gear rotation direction at the corner. In addition, the closed end that is closed on the side opposite to the opening end in the concave portion is located on the outer side in the radial direction from the bottom of the specific internal gear portion. The centrifugal force generated by the rotation of the specific rotating body during engine operation ensures that it flows into the open end and is pushed toward the closed end. According to the above, the foreign matter that has reached the corner where the flow direction of the lubricating liquid changes can be captured by being introduced into the recess regardless of the arrival position in the gear rotation direction. Accordingly, foreign matters such as abrasion powder are removed from the lubricating liquid without being restricted due to the supply performance of the lubricating liquid, and durability is improved.

請求項２に記載の発明によると、特定内歯車部の内周側において潤滑液は、入隅に向かう歯車軸方向へ流れる。このように、特定内歯車部の内周側において入隅に向かう歯車軸方向に流れた潤滑液は、入隅を形成する壁部により流れを遮られることで、流れ方向を壁部に沿う方向へと変化させる。このとき、入隅に向かって潤滑液と共に流れる異物は、入隅に向かって開口し特定内歯車部の歯底よりも凹んだ形となっている凹部に対し、内燃機関運転中の遠心力の作用によって確実に流入し得る。以上によれば、特定内歯車部と遊星歯車との噛合部分に発生した磨耗紛等の異物を潤滑液流れによって入隅へと運び、異物については凹部に捕捉させる一方、異物の除去された清浄な潤滑液を他の箇所まで供給可能となるので、耐久性の向上に貢献することができるのである。 According to the second aspect of the present invention, the lubricating liquid flows in the gear shaft direction toward the entrance corner on the inner peripheral side of the specific internal gear portion. As described above, the lubricating liquid that has flowed in the gear shaft direction toward the corner on the inner peripheral side of the specific internal gear portion is blocked by the wall portion that forms the corner, so that the flow direction is in the direction along the wall portion. To change. At this time, the foreign matter flowing together with the lubricating liquid toward the corner of the entrance is caused by the centrifugal force during operation of the internal combustion engine against the recess that is open toward the corner of the corner and is recessed from the tooth bottom of the specific internal gear portion. It can surely flow in by the action. According to the above, foreign matter such as wear powder generated at the meshing portion of the specific internal gear portion and the planetary gear is carried to the entrance corner by the flow of the lubricating liquid, and the foreign matter is trapped in the concave portion, while the foreign matter is removed As a result, it is possible to supply an appropriate lubricating liquid to other locations, which can contribute to an improvement in durability.

請求項３に記載の発明によると、凹部は、歯車軸方向に対し傾斜して設けられ、当該歯車軸方向において閉塞端が開口端よりも特定内歯車部とは反対側に位置する。これによれば、凹部へ流入した異物は、内燃機関運転中の遠心力の作用を受けることで、歯車軸方向の開口端よりも特定内歯車部と反対側に位置する開口端に向かって押し込まれることになる。このような凹部への押し込みにより捕捉された異物は、遠心力が作用する内燃機関の運転中は勿論、遠心力が消失する内燃機関の停止中にあっても、歯車軸方向に対し傾斜する凹部において開口端側には戻り難くなる。したがって、一旦凹部に捕捉された異物が開口端から入隅へ排出されて潤滑液に混入する事態を、内燃機関の作動状態に拘らず確実に抑制して高い耐久性を確保することができるのである。 According to the third aspect of the present invention, the recess is provided so as to be inclined with respect to the gear shaft direction, and the closed end is located on the opposite side of the opening end from the specific internal gear portion in the gear shaft direction. According to this, the foreign matter flowing into the recess is pushed toward the opening end located on the opposite side of the specific internal gear portion from the opening end in the gear shaft direction by receiving the action of centrifugal force during operation of the internal combustion engine. Will be. The foreign matter captured by the pushing into the concave portion is a concave portion that is inclined with respect to the gear shaft direction not only during operation of the internal combustion engine in which centrifugal force acts but also during stoppage of the internal combustion engine in which centrifugal force disappears. It becomes difficult to return to the opening end side. Therefore, it is possible to reliably suppress the foreign matter once captured in the recess from being discharged from the opening end to the corner and mixed into the lubricating liquid regardless of the operating state of the internal combustion engine, thereby ensuring high durability. is there.

請求項４に記載の発明によると、凹部は、開口端を形成すると共に軸方向に対し傾斜する傾斜部と、傾斜部に対し屈曲されると共に閉塞端を形成する屈曲部と、を有する。これによれば、凹部において開口端を形成する傾斜部から、閉塞端を形成する屈曲部へ内燃機関運転中の遠心力作用によって押し込まれた異物は、傾斜部に対する屈曲形状の屈曲部から当該傾斜部側には戻り難くなる。また、歯車軸方向に対し傾斜する傾斜部に異物が残存することになったとしても、当該残存異物は開口端側には戻り難くなる。したがって、一旦凹部に捕捉された異物が入隅へと排出されて潤滑液に混入する事態の抑制作用を、高めることができるのである。 According to a fourth aspect of the present invention, the recess has an inclined portion that forms an open end and is inclined with respect to the axial direction, and a bent portion that is bent with respect to the inclined portion and forms a closed end. According to this, the foreign matter pushed by the centrifugal force action during the operation of the internal combustion engine from the inclined portion forming the open end in the concave portion to the bent portion forming the closed end is inclined from the bent portion of the bent shape with respect to the inclined portion. It becomes difficult to return to the club side. Even if foreign matter remains on the inclined portion inclined with respect to the gear shaft direction, the residual foreign matter is difficult to return to the opening end side. Therefore, it is possible to enhance the suppression action of the situation where the foreign matter once captured in the recess is discharged to the corner and mixed into the lubricating liquid.

請求項５に記載の発明によると、凹部において屈曲部は、歯車軸方向において傾斜部よりも特定内歯車部とは反対側に閉塞端を形成する。このように、歯車軸方向において傾斜部よりも特定内歯車部とは反対側に閉塞端を形成する屈曲部では、傾斜部から押し込まれた異物を確実に捕捉することができる。したがって、一旦凹部に捕捉された異物が入隅に排出されて潤滑液に混入する事態の抑制作用を、さらに高めることができるのである。 According to the fifth aspect of the present invention, the bent portion in the concave portion forms a closed end on the opposite side of the inclined portion from the specific internal gear portion in the gear shaft direction. As described above, in the bent portion that forms the closed end on the side opposite to the specific internal gear portion with respect to the inclined portion in the gear shaft direction, the foreign matter pushed in from the inclined portion can be reliably captured. Therefore, it is possible to further enhance the action of suppressing the situation in which the foreign matter once captured in the recess is discharged into the corner and mixed into the lubricating liquid.

請求項６に記載の発明によると、特定回転体は、駆動側回転体及び従動側回転体の双方であるので、各回転体の内歯車部とその対応壁部との間の入隅に向かってそれぞれ開口する複数の凹部が設けられることになる。これによれば、各回転体の内歯車部及びその対応壁部間のいずれの入隅においても異物の滞留を抑制して、耐久性を高めることができるのである。 According to the invention described in claim 6, since the specific rotating body is both the driving side rotating body and the driven side rotating body, the specific rotating body is directed to the corner between the internal gear portion of each rotating body and its corresponding wall portion. Thus, a plurality of recesses each opening are provided. According to this, it is possible to suppress the staying of foreign matter at any corner between the internal gear portion of each rotating body and its corresponding wall portion, thereby improving durability.

請求項７に記載の発明のように、凹部よりも潤滑液流れの下流側に配置される軸受により駆動側回転体が軸受される構成では、凹部の開口する入隅から当該軸受に向かって流れる潤滑液が、凹部の捕捉作用によって異物の除去された清浄液となる。したがって、駆動側回転体を軸受する軸受に異物が侵入して耐久性を低下させる事態を、抑制することができるのである。 In the configuration in which the drive side rotating body is supported by the bearing disposed downstream of the concave portion with respect to the flow of the lubricating liquid as in the seventh aspect of the invention, it flows from the entrance corner where the concave portion opens toward the bearing. The lubricating liquid becomes a cleaning liquid from which foreign substances have been removed by the trapping action of the recesses. Therefore, it is possible to suppress a situation in which foreign matter enters the bearing that supports the drive-side rotator and deteriorates durability.

請求項８に記載の発明のように、凹部よりも潤滑液流れの下流側に配置される軸受により遊星歯車が軸受される構成では、凹部の開口する入隅から当該軸受に向かって流れる潤滑液が、凹部の捕捉作用によって異物の除去された清浄液となる。したがって、遊星歯車を軸受する軸受に異物が侵入して耐久性を低下させる事態を、抑制することができるのである。 In the configuration in which the planetary gear is supported by the bearing disposed downstream of the concave portion with respect to the flow of the lubricating liquid as in the invention according to the eighth aspect, the lubricating liquid flowing toward the bearing from the corner where the concave portion opens is provided. However, it becomes a cleaning liquid from which foreign substances are removed by the trapping action of the recesses. Therefore, it is possible to suppress a situation in which a foreign object enters a bearing for bearing the planetary gear to reduce durability.

請求項９に記載の発明のように、遊星キャリアを回転駆動して遊星歯車を遊星運動させるアクチュエータの回転軸体が、遊星歯車を遊星運動可能に支持する遊星キャリアと嵌合する構成では、嵌合界面のクリアランスにより回転軸体と遊星キャリアとを相対変位可能として、それら回転軸体及び遊星キャリア間の心ずれを吸収可能となる。またこのような構成において、請求項９に記載の発明によると、回転軸体と嵌合する遊星キャリアは凹部よりも潤滑液流れの下流側に配置されるので、凹部の開口する入隅から当該嵌合の界面に向かって流れる潤滑液は、凹部の捕捉作用によって異物の除去された清浄液となる。したがって、回転軸体及び遊星キャリアの嵌合界面に異物が侵入して耐久性を低下させる事態を、抑制することができるのである。 According to the ninth aspect of the present invention, in the configuration in which the rotating shaft body of the actuator that rotationally drives the planetary carrier to make the planetary gear move in a planetary manner is fitted with the planetary carrier that supports the planetary gear so that the planetary gear can move. The rotational shaft body and the planet carrier can be displaced relative to each other by the clearance at the interface, and the misalignment between the rotational shaft body and the planet carrier can be absorbed. Further, in such a configuration, according to the invention described in claim 9, since the planet carrier fitted to the rotating shaft body is disposed on the downstream side of the flow of the lubricating liquid from the recess, the planetary carrier is inserted from the entrance corner where the recess opens. The lubricating liquid flowing toward the fitting interface becomes a cleaning liquid from which foreign substances are removed by the trapping action of the recesses. Therefore, it is possible to suppress a situation in which foreign matter enters the fitting interface between the rotating shaft body and the planetary carrier to reduce durability.

以下、本発明の複数の実施形態を図面に基づいて説明する。尚、各実施形態において対応する構成要素には同一の符号を付すことにより、重複する説明を省略する。 Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description is abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment.

（第一実施形態）
図１は、本発明の第一実施形態によるバルブタイミング調整装置１を示している。バルブタイミング調整装置１は車両に搭載され、内燃機関のクランク軸（図示しない）からカム軸２へ機関トルクを伝達する伝達系に設置されている。尚、本実施形態においてカム軸２は、内燃機関の「動弁」のうち吸気弁（図示しない）を機関トルクの伝達によって開閉するものであり、バルブタイミング調整装置１は当該吸気弁のバルブタイミングを調整する。また、本実施形態において図１の左右方向は、水平面上におけるバルブタイミング調整装置１の水平方向と略一致している。 (First embodiment)
FIG. 1 shows a valve timing adjusting apparatus 1 according to a first embodiment of the present invention. The valve timing adjusting device 1 is mounted on a vehicle and installed in a transmission system that transmits engine torque from a crankshaft (not shown) of an internal combustion engine to a camshaft 2. In this embodiment, the camshaft 2 opens and closes an intake valve (not shown) of the “valve” of the internal combustion engine by transmitting the engine torque, and the valve timing adjusting device 1 controls the valve timing of the intake valve. Adjust. In the present embodiment, the left-right direction in FIG. 1 substantially coincides with the horizontal direction of the valve timing adjusting device 1 on a horizontal plane.

（基本構成）
以下、第一実施形態の基本構成について説明する。バルブタイミング調整装置１は、アクチュエータ４、通電制御回路部７及び位相調整機構８等を組み合わせてなる。 (Basic configuration)
Hereinafter, the basic configuration of the first embodiment will be described. The valve timing adjusting device 1 is a combination of an actuator 4, an energization control circuit unit 7, a phase adjusting mechanism 8, and the like.

アクチュエータ４は、例えばブラシレスモータ等の電動モータであり、内燃機関の固定節に固定されるケース５と、当該ケース５により正逆回転自在に支持される回転軸体６とを有している。通電制御回路部７は駆動ドライバ及びその制御用マイクロコンピュータ等から構成されており、ケース５の外部及び／又は内部に配置されてアクチュエータ４と電気的に接続されている。通電制御回路部７は、アクチュエータ４への通電を制御することにより回転軸体６を回転駆動する。 The actuator 4 is an electric motor such as a brushless motor, for example, and includes a case 5 fixed to a fixed node of the internal combustion engine and a rotating shaft body 6 supported by the case 5 so as to be rotatable forward and backward. The energization control circuit unit 7 includes a drive driver and a control microcomputer, and is disposed outside and / or inside the case 5 and electrically connected to the actuator 4. The energization control circuit unit 7 rotationally drives the rotating shaft body 6 by controlling energization to the actuator 4.

位相調整機構８は、駆動側回転体１０、従動側回転体２０、遊星キャリア４０及び遊星歯車５０を備えている。 The phase adjusting mechanism 8 includes a driving side rotating body 10, a driven side rotating body 20, a planet carrier 40, and a planetary gear 50.

図１〜３に示すように、駆動側回転体１０は全体として筒状を呈しており、位相調整機構８の他の構成要素２０，４０，５０を内部に収容している。駆動側回転体１０は、歯車部材１２及びスプロケット１３の間に筒壁部材１４を同軸上に共締めしてなる。 As shown in FIGS. 1 to 3, the drive side rotating body 10 has a cylindrical shape as a whole, and houses the other components 20, 40, 50 of the phase adjustment mechanism 8 therein. The drive-side rotator 10 is formed by coaxially fastening a cylindrical wall member 14 between a gear member 12 and a sprocket 13.

図１，２に示すように、歯車部材１２は有底円筒状を呈しており、歯底円の内周側に歯先円を有する駆動側内歯車部１８を周壁部によって形成している。図１，３に示すように、スプロケット１３は有底円筒状を呈しており、周壁部から径方向外側へ突出する歯１９を回転方向に複数有している。スプロケット１３は、それらの歯１９とクランク軸の複数の歯との間で環状のタイミングチェーン（図示しない）が掛け渡されることにより、クランク軸と連繋する。したがって、クランク軸から出力された機関トルクがタイミングチェーンを通じてスプロケット１３へ入力されるときには、駆動側回転体１０はクランク軸と連動して回転する。このとき駆動側回転体１０の回転方向は、図２の反時計方向及び図３の時計方向となる。 As shown in FIGS. 1 and 2, the gear member 12 has a bottomed cylindrical shape, and a driving side internal gear portion 18 having a tooth tip circle on the inner peripheral side of the root circle is formed by a peripheral wall portion. As shown in FIGS. 1 and 3, the sprocket 13 has a bottomed cylindrical shape, and has a plurality of teeth 19 protruding in the radial direction from the peripheral wall portion in the rotational direction. The sprocket 13 is linked to the crankshaft by passing an annular timing chain (not shown) between the teeth 19 and a plurality of teeth of the crankshaft. Therefore, when the engine torque output from the crankshaft is input to the sprocket 13 through the timing chain, the drive side rotator 10 rotates in conjunction with the crankshaft. At this time, the rotation direction of the drive-side rotator 10 is the counterclockwise direction of FIG. 2 and the clockwise direction of FIG.

図１，３に示すように、従動側回転体２０は有底円筒状を呈しており、それよりも大径円筒状の筒壁部材１４の内周側に同心上に配置されている。従動側回転体２０は、螺子止めによりカム軸２に同軸上に連結される連結壁部２１を、底壁部によって形成している。この連結により従動側回転体２０は、カム軸２と連動して回転可能且つ駆動側回転体１０に対して相対回転可能となっている。ここで、従動側回転体２０の回転方向は、駆動側回転体１０と同じ図３の時計方向に設定されている。 As shown in FIGS. 1 and 3, the driven-side rotator 20 has a bottomed cylindrical shape, and is concentrically disposed on the inner peripheral side of the cylindrical wall member 14 having a larger diameter than that. The driven-side rotating body 20 forms a connecting wall portion 21 that is coaxially connected to the camshaft 2 by screwing, with a bottom wall portion. By this connection, the driven-side rotator 20 can rotate in conjunction with the camshaft 2 and can rotate relative to the drive-side rotator 10. Here, the rotation direction of the driven-side rotator 20 is set in the clockwise direction in FIG.

従動側回転体２０の周壁部は、歯底円の内周側に歯先円を有する従動側内歯車部２２を形成している。ここで、従動側内歯車部２２の内径は駆動側内歯車部１８の内径よりも小さく設定され、また従動側内歯車部２２の歯数は駆動側内歯車部１８の歯数よりも少なく設定されている。従動側内歯車部２２は、駆動側内歯車部１８に対して軸方向へずれて配置されている。 The peripheral wall portion of the driven side rotating body 20 forms a driven side internal gear portion 22 having a tooth tip circle on the inner peripheral side of the root circle. Here, the inner diameter of the driven side internal gear portion 22 is set smaller than the inner diameter of the drive side internal gear portion 18, and the number of teeth of the driven side internal gear portion 22 is set smaller than the number of teeth of the drive side internal gear portion 18. Has been. The driven side internal gear portion 22 is arranged so as to be shifted in the axial direction with respect to the drive side internal gear portion 18.

図１〜３に示すように、遊星キャリア４０は全体として筒状を呈しており、内周面部によって入力部４１を形成している。入力部４１は、回転体１０，２０及び回転軸体６に対して同心上に配置されている。入力部４１には、回転軸体６に設けられた継手部４３と嵌合する嵌合溝４２が形成されている。この嵌合により遊星キャリア４０は、回転軸体６と連繋して一体に回転駆動可能となっており、また駆動側内歯車部１８に対して相対回転可能となっている。尚、ここで、回転軸体６を入力部４１と嵌合によって連繋させているのは、嵌合界面のクリアランスにより回転軸体６と遊星キャリア４０とを相対変位可能として、それら要素６，４０間の心ずれを吸収可能とするためである。 As shown in FIGS. 1 to 3, the planet carrier 40 has a cylindrical shape as a whole, and an input portion 41 is formed by an inner peripheral surface portion. The input unit 41 is arranged concentrically with the rotating bodies 10 and 20 and the rotating shaft body 6. The input portion 41 is formed with a fitting groove 42 that fits with a joint portion 43 provided on the rotary shaft body 6. By this fitting, the planetary carrier 40 is connected to the rotary shaft 6 and can be integrally rotated, and can be relatively rotated with respect to the drive-side internal gear portion 18. Here, the rotation shaft body 6 is connected to the input portion 41 by fitting because the rotation shaft body 6 and the planetary carrier 40 can be relatively displaced by the clearance of the fitting interface. This is because the misalignment between them can be absorbed.

図１に示すように遊星キャリア４０は、入力部４１と同心の外周面部によって回転体支持部４５を形成している。回転体支持部４５は、歯車部材１２の底壁部１６の中心孔１７を軸受する転がり軸受４６を介して、駆動側回転体１０を相対回転可能に支持している。また、図１〜３に示すように遊星キャリア４０は、入力部４１に対して偏心する外周面部によって遊星支持部４７を形成している。遊星支持部４７は、遊星歯車５０の中心孔５１を軸受する転がり軸受４８を介して、遊星歯車５０を遊星運動可能に支持している。ここで遊星運動とは、遊星歯車５０が遊星支持部４７の偏心中心線周りに自転しつつ、遊星キャリア４０の回転方向へ公転する遊星運動をいう。尚、本実施形態において転がり軸受４６，４８としては、開放型の玉軸受が用いられている。 As shown in FIG. 1, the planetary carrier 40 forms a rotating body support portion 45 by an outer peripheral surface portion concentric with the input portion 41. The rotator support 45 supports the drive-side rotator 10 through a rolling bearing 46 that supports the center hole 17 of the bottom wall 16 of the gear member 12 so as to be relatively rotatable. In addition, as shown in FIGS. 1 to 3, the planet carrier 40 forms a planet support portion 47 by an outer peripheral surface portion that is eccentric with respect to the input portion 41. The planetary support 47 supports the planetary gear 50 in a planetary manner via a rolling bearing 48 that supports the center hole 51 of the planetary gear 50. Here, the planetary movement refers to a planetary movement in which the planetary gear 50 revolves around the eccentric center line of the planetary support portion 47 and revolves in the rotation direction of the planetary carrier 40. In the present embodiment, open type ball bearings are used as the rolling bearings 46 and 48.

遊星歯車５０は段付円筒状に形成され、歯底円の外周側に歯先円を有する駆動側外歯車部５２及び従動側外歯車部５４を、それぞれ大径部分及び小径部分によって形成している。駆動側外歯車部５２及び従動側外歯車部５４の歯数は、それぞれ駆動側内歯車部１８及び従動側内歯車部２２の歯数よりも同数ずつ少なくなるように設定されている。駆動側外歯車部５２は、駆動側内歯車部１８の内周側に配置されて当該内歯車部１８と噛合している。また、駆動側外歯車部５２よりも連結壁部２１側の従動側外歯車部５４は、従動側内歯車部２２の内周側に配置されて当該内歯車部２２と噛合している。 The planetary gear 50 is formed in a stepped cylindrical shape, and a driving-side external gear portion 52 and a driven-side external gear portion 54 having a tip circle on the outer peripheral side of the root circle are formed by a large diameter portion and a small diameter portion, respectively. Yes. The number of teeth of the driving side external gear part 52 and the driven side external gear part 54 is set to be smaller by the same number than the number of teeth of the driving side internal gear part 18 and the driven side internal gear part 22, respectively. The drive side external gear portion 52 is disposed on the inner peripheral side of the drive side internal gear portion 18 and meshes with the internal gear portion 18. The driven-side external gear portion 54 closer to the connecting wall portion 21 than the drive-side external gear portion 52 is disposed on the inner peripheral side of the driven-side internal gear portion 22 and meshes with the internal gear portion 22.

このように回転体１０，２０間を歯車連繋してなる位相調整機構８は、駆動側回転体１０に対する従動側回転体２０の相対位相としての回転体間位相を、回転軸体６の回転状態に応じて調整する。 In this way, the phase adjustment mechanism 8 formed by linking the rotating bodies 10 and 20 with the gears uses the phase between the rotating bodies as the relative phase of the driven-side rotating body 20 with respect to the driving-side rotating body 10 as the rotational state of the rotating shaft body 6. Adjust according to.

具体的には、回転軸体６が駆動側回転体１０と同速回転することにより、遊星キャリア４０が駆動側内歯車部１８に対して相対回転しないときには、遊星歯車５０が遊星運動することなく回転体１０，２０と連れ回りする。したがって、回転体間位相は変化せず、それによってバルブタイミングが保持されることになる。 Specifically, when the rotating shaft body 6 rotates at the same speed as the driving side rotating body 10 and the planet carrier 40 does not rotate relative to the driving side internal gear portion 18, the planetary gear 50 does not perform planetary motion. It rotates with the rotating bodies 10 and 20. Therefore, the phase between the rotating bodies does not change, and thereby the valve timing is maintained.

一方、回転軸体６が駆動側回転体１０に対して高速回転することにより、遊星キャリア４０が駆動側内歯車部１８に対して進角側へ相対回転するときには、遊星歯車５０が遊星運動して従動側回転体２０が駆動側回転体１０に対する進角側へ相対回転する。したがって、回転体間位相は進角側へと変化し、それによってバルブタイミングが進角することになる。 On the other hand, when the rotating shaft body 6 rotates at high speed with respect to the driving side rotating body 10, the planetary gear 50 performs planetary motion when the planetary carrier 40 rotates relative to the driving side internal gear portion 18 toward the advance side. Thus, the driven-side rotator 20 rotates relative to the advance side with respect to the drive-side rotator 10. Therefore, the phase between the rotating bodies changes to the advance side, and thereby the valve timing advances.

また一方、回転軸体６が駆動側回転体１０に対して低速回転又は逆回転することにより、遊星キャリア４０が駆動側内歯車部１８に対して遅角側へ相対回転するときには、遊星歯車５０が遊星運動して従動側回転体２０が駆動側回転体１０に対して遅角側へ相対回転する。したがって、回転体間位相は遅角側へと変化し、それによってバルブタイミングが遅角することになる。 On the other hand, when the rotating shaft body 6 rotates at a low speed or reversely with respect to the driving side rotating body 10, the planetary gear 50 is rotated when the planetary carrier 40 rotates relative to the driving side internal gear portion 18 toward the retard side. As a result of the planetary movement, the driven-side rotator 20 rotates relative to the drive-side rotator 10 in the retarded direction. Therefore, the phase between the rotating bodies is changed to the retard side, and thereby the valve timing is retarded.

（特徴部分）
以下、第一実施形態の特徴部分について説明する。 (Characteristic part)
Hereinafter, the characteristic part of 1st embodiment is demonstrated.

（潤滑構造）
図４に示すように、金属製の従動側回転体２０においてカム軸２と当接する連結壁部２１の軸方向端面には、径方向へのびる形状の導入溝６０が形成されている。導入溝６０の径方向の内側端は、カム軸２に形成された搬送孔３に連通している。ここで搬送孔３は、「潤滑液」としての潤滑油を搬送するためのものであり、内燃機関用の潤滑油を吐出するポンプ９に接続されている。尚、本実施形態のポンプ９は、クランク軸によって駆動されるメカポンプであり、故に内燃機関の運転中は、作動油が継続して搬送孔３に圧送される一方、内燃機関の停止中は、搬送孔３への作動油の圧送がカットされることとなる。 (Lubricating structure)
As shown in FIG. 4, an introduction groove 60 having a shape extending in the radial direction is formed on the axial end surface of the connecting wall portion 21 in contact with the camshaft 2 in the metal driven rotating body 20. The radially inner end of the introduction groove 60 communicates with the conveyance hole 3 formed in the cam shaft 2. Here, the conveying hole 3 is for conveying lubricating oil as “lubricating liquid”, and is connected to a pump 9 for discharging lubricating oil for an internal combustion engine. The pump 9 of this embodiment is a mechanical pump that is driven by a crankshaft. Therefore, during operation of the internal combustion engine, hydraulic oil is continuously pumped to the transport hole 3, while the internal combustion engine is stopped. The pumping of the hydraulic oil to the transport hole 3 is cut.

駆動側回転体１０において、従動側回転体２０の導入溝６０側の端面に摺接する金属製スプロケット１３の軸方向端面には、回転方向に連続する同心円環状に環状溝６２が形成されている。これにより、環状溝６２の内周縁には、導入溝６０が径方向の外側端において連通している。 In the drive-side rotator 10, an annular groove 62 is formed on the end surface in the axial direction of the metal sprocket 13 that is in sliding contact with the end surface of the driven-side rotator 20 on the introduction groove 60 side. Thus, the introduction groove 60 communicates with the inner peripheral edge of the annular groove 62 at the radially outer end.

駆動側回転体１０において金属製の筒壁部材１４の内周面と従動側回転体２０の外周面との間には、径方向の隙間６４が軸方向全域に亘って形成されている。これにより、隙間６４の軸方向の一端は、環状溝６２の外周縁に連通している一方、隙間６４の軸方向の他端は、駆動側回転体１０の駆動側内歯車部１８と従動側回転体２０の従動側内歯車部２２とが軸方向に摺接する界面６６を通じて、それら内歯車部１８，２２の内周側と連通している。尚、ここで、駆動側内歯車部１８の内周側には、遊星歯車５０の駆動側外歯車部５２と転がり軸受４６，４８と遊星キャリア４０とが配置されており、また従動側内歯車部２２の内周側には、遊星歯車５０の従動側外歯車部５４と遊星キャリア４０と転がり軸受４８とが配置されている。 A radial gap 64 is formed across the entire axial direction between the inner peripheral surface of the metallic cylindrical wall member 14 and the outer peripheral surface of the driven-side rotator 20 in the drive-side rotator 10. Thus, one end in the axial direction of the gap 64 communicates with the outer peripheral edge of the annular groove 62, while the other end in the axial direction of the gap 64 is connected to the driving side internal gear portion 18 of the driving side rotating body 10 and the driven side. It communicates with the inner peripheral side of the internal gear portions 18 and 22 through an interface 66 in which the driven side internal gear portion 22 of the rotating body 20 is in sliding contact with the axial direction. Here, on the inner peripheral side of the drive side internal gear portion 18, the drive side external gear portion 52 of the planetary gear 50, the rolling bearings 46 and 48, and the planetary carrier 40 are arranged, and the driven side internal gear is also provided. On the inner peripheral side of the portion 22, a driven-side outer gear portion 54 of the planetary gear 50, the planet carrier 40, and a rolling bearing 48 are arranged.

このような構成により内燃機関の運転中には、図５に示すように搬送孔３に圧送された潤滑油が導入溝６０に導入され、さらに環状溝６２、隙間６４及び界面６６を順次経由して駆動側内歯車部１８及び従動側内歯車部２２の内周側へと供給される。駆動側内歯車部１８の内周側へ供給された潤滑油は、当該内歯車部１８と駆動側外歯車部５２との間を軸方向へ通過した後、その一部が転がり軸受４６の内部を通過して装置１の外部へ排出される一方、残部が転がり軸受４８の内部を通過する。また、従動側内歯車部２２の内周側へ供給された潤滑油は、当該内歯車部２２と従動側外歯車部５４との間を軸方向へ通過した後、転がり軸受４８内部を通過した潤滑油と共に遊星キャリア４０の内周側へ流入して、入力部４１と回転軸体６との嵌合部分を通過する。 With this configuration, during operation of the internal combustion engine, as shown in FIG. 5, the lubricating oil pumped to the transport hole 3 is introduced into the introduction groove 60, and further sequentially passes through the annular groove 62, the gap 64 and the interface 66. Then, it is supplied to the inner peripheral side of the driving side internal gear portion 18 and the driven side internal gear portion 22. The lubricating oil supplied to the inner peripheral side of the drive-side internal gear portion 18 passes between the internal gear portion 18 and the drive-side external gear portion 52 in the axial direction, and then a part thereof is inside the rolling bearing 46. And the remaining part passes through the inside of the rolling bearing 48. Further, the lubricating oil supplied to the inner peripheral side of the driven side internal gear portion 22 passes between the internal gear portion 22 and the driven side external gear portion 54 in the axial direction and then passes through the inside of the rolling bearing 48. It flows into the inner peripheral side of the planet carrier 40 together with the lubricating oil and passes through the fitting portion between the input portion 41 and the rotating shaft body 6.

以上により内燃機関の運転中は、歯車部１８，５２の噛合部分、歯車部２２，５４の噛合部分、転がり軸受４６，４８の内部並びに入力部４１と回転軸体６との嵌合部分が、潤滑油の通過に伴って潤滑されることになるのである。 As described above, during operation of the internal combustion engine, the meshing portion of the gear portions 18 and 52, the meshing portion of the gear portions 22 and 54, the inside of the rolling bearings 46 and 48, and the fitting portion of the input portion 41 and the rotary shaft body 6 are It is lubricated as the lubricating oil passes.

（異物捕捉構造）
図４に示すように、駆動側回転体１０の金属製の歯車部材１２には、回転方向に連続する同心円環状に駆動側凹部７０が形成されている。具体的に駆動側凹部７０は、歯車部材１２において駆動側内歯車部１８と軸方向に隣接する底壁部１６が当該内歯車部１８の各歯１８ａとの間に略直角に形成する入隅７２に向かって、開口している。また、駆動側凹部７０は、縦断面（図４に示す断面）において軸方向に対する傾斜方向に凹んでおり、閉塞された閉塞端７０ｂを当該傾斜方向において開口端７０ａとは反対側に形成している。そして、図２，４に示すように本実施形態の駆動側凹部７０は、各歯１８ａの歯底の最深部を結んだ駆動側内歯車部１８の歯底円Ｃｄよりも径方向の外側に且つ軸方向において開口端７０ａよりも駆動側内歯車部１８とは反対側に、閉塞端７０ｂが位置する形となっている。 (Foreign matter capturing structure)
As shown in FIG. 4, a drive-side recess 70 is formed on the metal gear member 12 of the drive-side rotator 10 in a concentric annular shape that is continuous in the rotation direction. Specifically, the drive-side recess 70 is a corner formed by the bottom wall portion 16 adjacent to the drive-side internal gear portion 18 in the gear member 12 in the axial direction between the teeth 18a of the internal gear portion 18 at a substantially right angle. Opening toward 72. Further, the drive-side recess 70 is recessed in an inclination direction with respect to the axial direction in a longitudinal section (section shown in FIG. 4), and a closed end 70b is formed on the opposite side of the opening end 70a in the inclination direction. Yes. As shown in FIGS. 2 and 4, the drive-side recess 70 of the present embodiment is more radially outward than the root circle Cd of the drive-side internal gear portion 18 that connects the deepest portions of the roots of the teeth 18 a. In addition, the closed end 70b is positioned on the opposite side of the driving end internal gear portion 18 from the opening end 70a in the axial direction.

図５に示すように、駆動側内歯車部１８とその内周側の駆動側外歯車部５２との間を入隅７２に向かう軸方向へ流れる潤滑油は、駆動側内歯車部１８に略直角の底壁部１６によって流れを遮られる。その結果、潤滑油の流れ方向は、底壁部１６に沿った径方向の内側となる転がり軸受４６の配置側へ変化することになる。 As shown in FIG. 5, the lubricating oil flowing in the axial direction toward the corner 72 between the drive-side internal gear portion 18 and the drive-side external gear portion 52 on the inner peripheral side thereof is substantially transferred to the drive-side internal gear portion 18. The flow is blocked by the right bottom wall 16. As a result, the flow direction of the lubricating oil changes to the arrangement side of the rolling bearing 46 that is radially inward along the bottom wall portion 16.

このとき、歯車部１８，５２の噛合部分に発生の磨耗紛等の異物は、潤滑油と共に入隅７２に向かって流れることになるが、入隅７２に到達した異物は、当該入隅７２に開口し回転方向に連続する駆動側凹部７０の開口端７０ａへ回転方向の任意箇所から流入し得る。またこのとき、駆動側内歯車部１８の歯底円Ｃｄ（図４参照）よりも径方向の外側に閉塞端７０ｂを有する駆動側凹部７０には、各歯１８ａの歯底が露出する入隅７２の異物が、内燃機関運転中の駆動側回転体１０に生じる遠心力作用を受けて確実に流入し、閉塞端７０ｂ側へと押し込まれる。しかも、図５の如く水平面上の水平方向（同図の左右方向）と略一致する軸方向に対して傾斜した駆動側凹部７０においては、遠心力及び重力が径方向に作用する内燃機関の運転中は勿論、遠心力が消失して重力のみが作用する内燃機関の停止中にあっても、異物が開口端７０ａ側に戻り難くなる。 At this time, foreign matter such as abrasion powder generated at the meshing portions of the gear portions 18 and 52 flows toward the corner 72 together with the lubricating oil. However, the foreign matter that has reached the corner 72 enters the corner 72. It can flow into the opening end 70a of the drive-side recess 70 that is open and continuous in the rotational direction from any location in the rotational direction. Further, at this time, in the drive-side recess 70 having the closed end 70b on the outer side in the radial direction from the root circle Cd (see FIG. 4) of the drive-side internal gear portion 18, the corner where the tooth bottom of each tooth 18a is exposed. The foreign matter 72 is surely inflowed by the action of the centrifugal force generated in the drive side rotating body 10 during operation of the internal combustion engine, and is pushed into the closed end 70b side. Moreover, in the drive-side recess 70 inclined with respect to the axial direction substantially coincident with the horizontal direction on the horizontal plane (the left-right direction in the figure) as shown in FIG. 5, the operation of the internal combustion engine in which centrifugal force and gravity act in the radial direction. Of course, even when the internal combustion engine where the centrifugal force disappears and only gravity acts is stopped, the foreign matter is difficult to return to the opening end 70a side.

これらのことから、潤滑油と共に入隅７２に到達した異物については、回転方向の到達位置に拘らず駆動側凹部７０に確実に捕捉し、またそれによって異物の除去された清浄な潤滑油については、転がり軸受４６，４８の側へと供給できるのである。 For these reasons, the foreign matter that has reached the corner 72 together with the lubricating oil is reliably captured in the drive-side recess 70 regardless of the position reached in the rotational direction, and the clean lubricating oil from which the foreign matter has been removed is thereby obtained. The roller bearings 46 and 48 can be supplied.

ここまで説明の駆動側凹部７０に対応して従動側回転体２０には、図４に示すように、回転方向に連続する同心円環状の従動側凹部８０が形成されている。具体的に従動側凹部８０は、従動側回転体２０において従動側内歯車部２２と軸方向に隣接する連結壁部２１が当該内歯車部２２の各歯２２ａとの間に略直角に形成する入隅８２に向かって、開口している。また、従動側凹部８０は、従動側内歯車部２２の縦断面（即ち、図４に示す断面）において軸方向に対する傾斜方向に凹んでおり、閉塞された閉塞端８０ｂを当該傾斜方向において開口端８０ａとは反対側に形成している。そして、図３，４に示すように本実施形態の従動側凹部８０は、各歯２２ａの歯底の最深部を結んだ従動側内歯車部２２の歯底円Ｃｆよりも径方向の外側に且つ軸方向において開口端８０ａよりも従動側内歯車部２２とは反対側に、閉塞端８０ｂが位置する形となっている。 Corresponding to the driving side recess 70 described so far, the driven side rotating body 20 is formed with a concentric annular driven side recess 80 continuous in the rotation direction, as shown in FIG. Specifically, the driven-side recess 80 is formed in the driven-side rotating body 20 between the driven-side internal gear portion 22 and the connecting wall portion 21 adjacent in the axial direction at a substantially right angle between the teeth 22 a of the internal gear portion 22. It opens toward the entrance corner 82. Further, the driven-side recess 80 is recessed in the direction of inclination with respect to the axial direction in the longitudinal section of the driven-side internal gear section 22 (that is, the cross section shown in FIG. 4), and the closed end 80b is opened to the open end in the direction of inclination. It is formed on the opposite side to 80a. As shown in FIGS. 3 and 4, the driven-side concave portion 80 of the present embodiment is more radially outward than the root circle Cf of the driven-side internal gear portion 22 that connects the deepest portions of the roots of the teeth 22 a. In addition, the closed end 80b is located on the opposite side of the driven side internal gear portion 22 from the open end 80a in the axial direction.

図５に示すように、従動側内歯車部２２とその内周側の従動側外歯車部５４との間を入隅８２に向かう軸方向へ流れる潤滑油は、従動側内歯車部２２に略直角の連結壁部２１によって流れを遮られる。その結果、潤滑油の流れ方向は、連結壁部２１に沿った径方向の内側となる遊星キャリア４０及び転がり軸受４８の配置側へ変化することになる。 As shown in FIG. 5, the lubricating oil flowing in the axial direction toward the corner 82 between the driven-side internal gear portion 22 and the driven-side external gear portion 54 on the inner peripheral side thereof is substantially transferred to the driven-side internal gear portion 22. The flow is blocked by the right-angle connecting wall portion 21. As a result, the flow direction of the lubricating oil changes to the arrangement side of the planetary carrier 40 and the rolling bearing 48 that are radially inside along the connecting wall portion 21.

このとき、歯車部２２，５４の噛合部分に発生の磨耗紛等の異物は、潤滑油と共に入隅８２に向かって流れることになるが、入隅８２に到達した異物は、当該入隅８２に開口し回転方向に連続する従動側凹部８０の開口端８０ａへ回転方向の任意箇所から流入し得る。またこのとき、従動側内歯車部２２の歯底円Ｃｆ（図４参照）よりも径方向の外側に閉塞端８０ｂを有する従動側凹部８０には、各歯２２ａの歯底が露出する入隅８２の異物が、内燃機関運転中に従動側回転体２０に生じる遠心力作用を受けて確実に流入し、閉塞端８０ｂ側へと押し込まれる。しかも、駆動側凹部７０の場合と同様に軸方向に対して傾斜した従動側凹部８０においては、内燃機関の運転中のみならず内燃機関の停止中にあっても、異物が開口端８０ａ側に戻り難くなる。 At this time, foreign matter such as wear powder generated in the meshing portions of the gear portions 22 and 54 flows toward the entrance corner 82 together with the lubricating oil, but the foreign matter that has reached the entrance corner 82 enters the entrance corner 82. It can flow into the opening end 80a of the driven recess 80 that opens and continues in the rotational direction from any location in the rotational direction. Further, at this time, in the driven-side concave portion 80 having the closed end 80b on the outer side in the radial direction from the root circle Cf (see FIG. 4) of the driven-side internal gear portion 22, the corner where the tooth bottom of each tooth 22a is exposed. The foreign matter 82 is reliably inflowed by the centrifugal force action generated in the driven-side rotator 20 during operation of the internal combustion engine, and is pushed into the closed end 80b. In addition, in the driven recess 80 that is inclined with respect to the axial direction as in the case of the drive recess 70, the foreign matter moves toward the opening end 80a not only during the operation of the internal combustion engine but also when the internal combustion engine is stopped. It becomes difficult to return.

これらのことから、潤滑油と共に入隅８２に到達した異物についても、回転方向の到達位置に拘らず従動側凹部８０に確実に捕捉し、またそれによって異物の除去された清浄な潤滑油については、遊星キャリア４０及び転がり軸受４８の配置側へと供給できるのである。 For these reasons, the foreign matter that has reached the corner 82 together with the lubricating oil is surely captured in the driven-side concave portion 80 regardless of the position reached in the rotational direction, and the clean lubricating oil from which the foreign matter has been removed is thereby obtained. The planetary carrier 40 and the rolling bearing 48 can be supplied to the arrangement side.

以上説明した第一実施形態によれば、各凹部７０，８０により異物の捕捉作用を発揮して、それら凹部７０，８０よりも下流側へ供給される潤滑油をポンプ９の性能如何に拘らず清浄に保つことができる。したがって、凹部７０，８０の下流側に配置された転がり軸受４６，４８の内部や、凹部８０の下流側に配置された遊星キャリア４０と回転軸体６との嵌合部分に異物が侵入して耐久性の低下を招く事態に対して、高い抑制効果を発揮することが可能となる。 According to the first embodiment described above, the foreign substances are captured by the concave portions 70 and 80, and the lubricating oil supplied to the downstream side of the concave portions 70 and 80 is supplied regardless of the performance of the pump 9. Can be kept clean. Therefore, foreign matter enters the inside of the rolling bearings 46, 48 disposed on the downstream side of the recesses 70, 80 and the fitting portion between the planetary carrier 40 and the rotating shaft body 6 disposed on the downstream side of the recess 80. It is possible to exert a high suppression effect against a situation that causes a decrease in durability.

尚、ここまでの第一実施形態では、駆動側回転体１０及び従動側回転体２０がそれぞれ特許請求の範囲に記載の「特定回転体」に相当し、駆動側内歯車部１８及び従動側内歯車部２２がそれぞれ特許請求の範囲に記載の「特定内歯車部」に相当し、駆動側凹部７０及び従動側凹部８０がそれぞれ特許請求の範囲に記載の「凹部」に相当し、歯車部材１２の底壁部１６及び従動側回転体２０の底壁部からなる連結壁部２１がそれぞれ特許請求の範囲に記載の「壁部」に相当し、ポンプ９が特許請求の範囲に記載の「供給源」に相当し、転がり軸受４６が特許請求の範囲に記載の「駆動側回転体を軸受する軸受」に相当し、転がり軸受４８が特許請求の範囲に記載の「遊星歯車を軸受する軸受」に相当している。 In the first embodiment so far, the driving side rotating body 10 and the driven side rotating body 20 correspond to the “specific rotating body” described in the claims, respectively, and the driving side internal gear portion 18 and the driven side internal body are the same. Each of the gear portions 22 corresponds to a “specific internal gear portion” described in the claims, and each of the driving-side concave portion 70 and the driven-side concave portion 80 corresponds to a “concave portion” described in the claims, and the gear member 12. The connecting wall portion 21 composed of the bottom wall portion 16 and the bottom wall portion of the driven-side rotator 20 corresponds to the “wall portion” recited in the claims, and the pump 9 includes the “supply” recited in the claims. The rolling bearing 46 corresponds to a “bearing for bearing a drive side rotating body” described in the claims, and the rolling bearing 48 corresponds to a “bearing for bearing planetary gears” in the claims. It corresponds to.

（第二実施形態）
図６に示すように、本発明の第二実施形態は第一実施形態の変形例である。第二実施形態の駆動側凹部１７０は、傾斜部１７４と屈曲部１７６とから構成されている。具体的に傾斜部１７４は、第一実施形態の駆動側凹部７０に準ずる形状、即ち駆動側内歯車部１８の回転方向に連続して開口端７０ａを形成し且つ縦断面（図６に示す断面）において駆動側内歯車部１８の軸方向に対して傾斜する円環状に、形成されている。また、屈曲部１７６は、縦断面において傾斜部１７４に対する屈曲形状をなし且つ駆動側内歯車部１８の回転方向に連続して閉塞端７０ｂを形成する円環状に、形成されている。ここで、特に本実施形態の屈曲部１７６は、傾斜部１７４に対し駆動側内歯車部１８の軸方向に沿って当該内歯車部１８とは反対側に屈曲された形状を、縦断面において有している。これにより屈曲部１７６は、軸方向において傾斜部１７４よりも駆動側内歯車部１８とは反対側に閉塞端７０ｂを形成する形となっている。尚、こうした形状の駆動側凹部１７０が設けられる歯車部材１２については、例えば図６に示すように、凹部１７０の内周側の内壁面及び閉塞端７０ｂを形成する部材を、凹部１７０の外周側の内壁面を形成する部材に螺子留めして結合すること等によって、実現される。 (Second embodiment)
As shown in FIG. 6, the second embodiment of the present invention is a modification of the first embodiment. The drive-side recess 170 of the second embodiment includes an inclined part 174 and a bent part 176. Specifically, the inclined portion 174 has a shape similar to that of the driving-side concave portion 70 of the first embodiment, that is, forms an open end 70a continuously in the rotational direction of the driving-side internal gear portion 18, and is a longitudinal section (the section shown in FIG. ) In an annular shape inclined with respect to the axial direction of the drive-side internal gear portion 18. Further, the bent portion 176 is formed in an annular shape that forms a bent shape with respect to the inclined portion 174 in the longitudinal section and continuously forms the closed end 70b in the rotation direction of the drive side internal gear portion 18. Here, in particular, the bent portion 176 of the present embodiment has a shape that is bent in the longitudinal direction in the axial direction of the drive side internal gear portion 18 with respect to the inclined portion 174 in a direction opposite to the internal gear portion 18. is doing. As a result, the bent portion 176 forms a closed end 70b on the opposite side of the drive-side internal gear portion 18 from the inclined portion 174 in the axial direction. For example, as shown in FIG. 6, the gear member 12 provided with the drive-side recess 170 having such a shape is a member that forms the inner wall surface and the closed end 70 b on the inner periphery side of the recess 170. This is realized by, for example, screwing and joining to a member forming the inner wall surface.

このような駆動側凹部１７０に対応して本実施形態では、従動側凹部１８０も傾斜部１８４と屈曲部１８６とから構成されている。具体的に傾斜部１８４は、第一実施形態の従動側凹部８０に準ずる形状、即ち従動側内歯車部２２の回転方向に連続して開口端８０ａを形成し且つ縦断面（図６に示す断面）において従動側内歯車部２２の軸方向に対して傾斜する円環状に、形成されている。また、屈曲部１８６は、縦断面において傾斜部１８４に対する屈曲形状をなし且つ従動側内歯車部２２の回転方向に連続して閉塞端８０ｂを形成する円環状に、形成されている。ここで、従動側凹部１８０の屈曲部１８６については、傾斜部１８４に対し従動側内歯車部２２の軸方向に沿って当該内歯車部２２とは反対側に屈曲された形状を、縦断面において有している。これにより屈曲部１８６は、軸方向において傾斜部１８４よりも従動側内歯車部２２とは反対側に閉塞端８０ｂを形成する形となっている。尚、こうした形状の従動側凹部１８０が設けられる従動側回転体２０については、例えば図６に示すように、凹部１８０の内周側の内壁面及び閉塞端８０ｂを形成する部材を、凹部１８０の外周側の内壁面を形成する部材に圧入して結合すること等によって、実現される。 Corresponding to such a driving-side recess 170, in this embodiment, the driven-side recess 180 is also composed of an inclined portion 184 and a bent portion 186. Specifically, the inclined portion 184 has a shape similar to the driven-side concave portion 80 of the first embodiment, that is, forms an open end 80a continuously in the rotational direction of the driven-side internal gear portion 22, and is a longitudinal section (the section shown in FIG. 6). ) In an annular shape inclined with respect to the axial direction of the driven side internal gear portion 22. Further, the bent portion 186 is formed in an annular shape that has a bent shape with respect to the inclined portion 184 in the longitudinal section and continuously forms the closed end 80b in the rotational direction of the driven side internal gear portion 22. Here, the bent portion 186 of the driven-side concave portion 180 has a shape that is bent in the longitudinal direction in the axial direction of the driven-side internal gear portion 22 with respect to the inclined portion 184 in the longitudinal direction. Have. As a result, the bent portion 186 forms a closed end 80b on the opposite side of the driven side internal gear portion 22 from the inclined portion 184 in the axial direction. For the driven-side rotating body 20 provided with the driven-side concave portion 180 having such a shape, for example, as shown in FIG. 6, the members forming the inner wall surface on the inner peripheral side of the concave portion 180 and the closed end 80 b are used. This is realized by, for example, press-fitting into a member that forms the inner wall surface on the outer peripheral side and coupling.

以上説明した構成の第二実施形態では、各凹部１７０，１８０において対応する入隅７２，８２から開口端７０ａ，８０ａへ流入した異物は、内燃機関運転中の遠心力作用によって傾斜部１７４，１８４から屈曲部１７６，１８６へと押し込まれることになる。このようにして、傾斜部１７４，１８４に対する屈曲形状の屈曲部１７６，１８６へ押し込まれた異物は、内燃機関の運転中のみならず、内燃機関の停止中においても、傾斜部１７４，１８４側には戻り難くなる。ここで特に、軸方向の傾斜部１７４，１８４よりも内歯車部１８，２２とは反対側に且つ歯底円Ｃｄ，Ｃｆよりも径方向の外側に閉塞端７０ｂ，８０ｂを形成する屈曲部１７６，１８６では、入り込んだ異物を確実に捕捉しておくことができる。また、仮に傾斜部１７４，１８４に異物が残存することになったとしても、当該残存異物は、第一実施形態の凹部７０，８０の場合と同様に開口端７０ａ，８０ａ側には戻り難くなる。これらのことから、第二実施形態によれば、一旦凹部１７０，１８０に捕捉された異物が入隅７２，８２へと排出されて潤滑油に混入する事態を回避し、それによって耐久性の向上に大きく貢献することが可能となるのである。 In the second embodiment having the above-described configuration, the foreign matter that has flowed into the opening ends 70a and 80a from the corresponding corners 72 and 82 in the recesses 170 and 180 is inclined by the centrifugal force during operation of the internal combustion engine 174 and 184. Will be pushed into the bent portions 176, 186. In this manner, the foreign matter pushed into the bent portions 176 and 186 having a bent shape with respect to the inclined portions 174 and 184 is not only during the operation of the internal combustion engine but also on the inclined portions 174 and 184 side even when the internal combustion engine is stopped. Is difficult to return. In particular, a bent portion 176 that forms closed ends 70b and 80b on the opposite side of the internal gear portions 18 and 22 from the inclined portions 174 and 184 in the axial direction and on the outer side in the radial direction of the root circles Cd and Cf. , 186 can reliably capture the foreign matter that has entered. Further, even if foreign matter remains in the inclined portions 174 and 184, the residual foreign matter is unlikely to return to the opening ends 70a and 80a as in the case of the concave portions 70 and 80 of the first embodiment. . For these reasons, according to the second embodiment, it is possible to avoid a situation in which foreign matter once captured in the recesses 170 and 180 is discharged into the corners 72 and 82 and mixed into the lubricating oil, thereby improving durability. It is possible to greatly contribute to

尚、ここまでの第二実施形態では、駆動側凹部１７０及び従動側凹部１８０がそれぞれ特許請求の範囲に記載の「凹部」に相当している。 In the second embodiment thus far, each of the driving side concave portion 170 and the driven side concave portion 180 corresponds to a “concave portion” described in the claims.

（他の実施形態）
以上、本発明の複数の実施形態について説明したが、本発明はそれらの実施形態に限定して解釈されるものではなく、その要旨を逸脱しない範囲内において種々の実施形態に適用することができる。 (Other embodiments)
Although a plurality of embodiments of the present invention have been described above, the present invention is not construed as being limited to these embodiments, and can be applied to various embodiments without departing from the scope of the present invention. .

例えば第一及び第二実施形態では、駆動側凹部７０，１７０と従動側凹部８０，１８０のうちいずれか一方を設けないようにしてもよい。また、第一実施形態では、図７に変形例を示すように各凹部７０，８０の閉塞端７０ｂ，８０ｂを開口端７０ａ，８０ａと径方向に重ねて位置させてもよく、それに準じて第二実施形態では、各凹部１７０，１８０の屈曲部１７６，１８６において閉塞端７０ｂ，８０ｂとは反対側端を開口端７０ａ，８０ａと径方向に重ねて位置させてもよい。さらに第二実施形態では、駆動側凹部１７０の代わりに第一実施形態の駆動側凹部７０を設けてもよいし、あるいは従動側凹部１８０の代わりに第一実施形態の従動側凹部８０を設けるようにしてもよい。またさらに第一及び第二実施形態では、従動側回転体２０の連結壁部２１を貫通して搬送孔３に連通する貫通孔を設けること等により、各内歯車部１８，２２の内周側における潤滑油の流れ方向を入隅７２，８２とは反対側に向かう軸方向としてもよい。尚、この場合に潤滑油は、壁部１６，２１に沿って径方向内側から入隅７２，８２へ供給される形態となる。 For example, in the first and second embodiments, any one of the driving side recesses 70 and 170 and the driven side recesses 80 and 180 may not be provided. In the first embodiment, the closed ends 70b, 80b of the recesses 70, 80 may be positioned so as to overlap the open ends 70a, 80a in the radial direction as shown in FIG. In the second embodiment, the opposite ends of the bent portions 176 and 186 of the concave portions 170 and 180 from the closed ends 70b and 80b may be positioned so as to overlap the open ends 70a and 80a in the radial direction. Further, in the second embodiment, the driving side recess 70 of the first embodiment may be provided instead of the driving side recess 170, or the driven side recess 80 of the first embodiment may be provided instead of the driven side recess 180. It may be. Furthermore, in the first and second embodiments, the inner peripheral side of each internal gear portion 18, 22 is provided by providing a through hole that penetrates the connecting wall portion 21 of the driven side rotating body 20 and communicates with the conveying hole 3. The flow direction of the lubricating oil may be an axial direction toward the opposite side to the corners 72 and 82. In this case, the lubricating oil is supplied from the radially inner side to the corners 72 and 82 along the walls 16 and 21.

加えて第一及び第二実施形態では、駆動側内歯車部１８及び従動側内歯車部２２の径並びに歯数について、相対比が説明のものと反対となるように設定してもよい。また加えて第一及び第二実施形態では、転がり軸受４６，４８の少なくとも一方を設けないで、駆動側回転体１０及び遊星歯車５０の少なくとも一方を、遊星キャリア４０に設けた滑り軸受により支持するようにしてもよい。さらに加えて第一及び第二実施形態では、転がり軸受４６，４８の少なくとも一方として、例えばころ軸受を用いてもよく、またいずれの種類の場合でも、潤滑液を予封入した封入型の転がり軸受を用いてもよい。またさらに加えて第一及び第二実施形態では、アクチュエータ４として、例えば電磁式ブレーキ又は流体式ブレーキ等の電動ブレーキや、油圧モータを用いてもよい。 In addition, in the first and second embodiments, the diameter and the number of teeth of the driving side internal gear portion 18 and the driven side internal gear portion 22 may be set so that the relative ratio is opposite to that described. In addition, in the first and second embodiments, at least one of the rolling bearings 46 and 48 is not provided, and at least one of the drive side rotating body 10 and the planetary gear 50 is supported by a slide bearing provided on the planet carrier 40. You may do it. In addition, in the first and second embodiments, for example, a roller bearing may be used as at least one of the rolling bearings 46 and 48. In any case, an encapsulated type rolling bearing in which a lubricant is pre-encapsulated. May be used. In addition, in the first and second embodiments, the actuator 4 may be an electric brake such as an electromagnetic brake or a fluid brake, or a hydraulic motor.

そして、本発明は、第一及び第二実施形態のように吸気弁のバルブタイミングを調整する装置以外にも、「動弁」としての排気弁のバルブタイミングを調整する装置や、吸気弁及び排気弁の双方のバルブタイミングを調整する装置に適用することができる。 In addition to the device for adjusting the valve timing of the intake valve as in the first and second embodiments, the present invention also includes a device for adjusting the valve timing of the exhaust valve as a “valve”, an intake valve, and an exhaust valve. The present invention can be applied to a device that adjusts the valve timing of both valves.

本発明の第一実施形態によるバルブタイミング調整装置の基本構成を示す図であって、図２のI−I線断面図である。It is a figure which shows the basic composition of the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. 図１のII−II線断面図である。It is the II-II sectional view taken on the line of FIG. 図１のIII−III線断面図である。It is the III-III sectional view taken on the line of FIG. 図１の位相調整機構を拡大して示す断面図である。It is sectional drawing which expands and shows the phase adjustment mechanism of FIG. 図４に示す位相調整機構における潤滑油流れについて説明するための模式図である。It is a schematic diagram for demonstrating the lubricating oil flow in the phase adjustment mechanism shown in FIG. 本発明の第二実施形態によるバルブタイミング調整装置の位相調整機構を拡大して示す断面図である。It is sectional drawing which expands and shows the phase adjustment mechanism of the valve timing adjustment apparatus by 2nd embodiment of this invention. 図１の位相調整機構の変形例を拡大して示す断面図である。It is sectional drawing which expands and shows the modification of the phase adjustment mechanism of FIG.

符号の説明Explanation of symbols

１バルブタイミング調整装置、２カム軸、３搬送孔、４アクチュエータ、６回転軸体、７通電制御回路部、８位相調整機構、９ポンプ（供給源）、１０駆動側回転体（特定回転体）、１２歯車部材、１３スプロケット、１４筒壁部材、１６底壁部（壁部）、１７中心孔、１８駆動側内歯車部（特定内歯車部）、１８ａ歯、２０従動側回転体（特定回転体）、２１連結壁部（壁部）、２２従動側内歯車部（特定内歯車部）、２２ａ歯、４０遊星キャリア、４１入力部、４２嵌合溝、４３継手部、４５回転体支持部、４６転がり軸受（軸受）、４８転がり軸受（軸受）４７遊星支持部、５０遊星歯車、５１中心孔、５２駆動側外歯車部、５４従動側外歯車部、６０導入溝、６２環状溝、６４隙間、６６界面、７０，１７０駆動側凹部（凹部）、７０ａ，８０ａ開口端、７０ｂ，８０ｂ閉塞端、７２，８２入隅、８０，１８０従動側凹部（凹部）、１７４，１８４傾斜部、１７６，１８６屈曲部、Ｃｄ，Ｃｆ歯底円 DESCRIPTION OF SYMBOLS 1 Valve timing adjustment device, 2 Cam shaft, 3 Conveying hole, 4 Actuator, 6 Rotating shaft body, 7 Current supply control circuit part, 8 Phase adjustment mechanism, 9 Pump (supply source), 10 Drive side rotating body (specific rotating body) , 12 gear member, 13 sprocket, 14 cylindrical wall member, 16 bottom wall portion (wall portion), 17 center hole, 18 driving side internal gear portion (specific internal gear portion), 18a tooth, 20 driven side rotating body (specific rotation) Body), 21 connecting wall portion (wall portion), 22 driven side internal gear portion (specific internal gear portion), 22a tooth, 40 planet carrier, 41 input portion, 42 fitting groove, 43 joint portion, 45 rotating body support portion , 46 Rolling bearing (bearing), 48 Rolling bearing (bearing) 47 Planetary support part, 50 planetary gear, 51 center hole, 52 driving side external gear part, 54 driven side external gear part, 60 introduction groove, 62 annular groove, 64 Gap , 66 interface, 70, 170 drive side recess (recess), 70a, 80a open end, 70b, 80b closed end, 72, 82 corner, 80, 180 driven recess (recess), 174, 184 inclined part, 176 186 bent part, Cd, Cf root circle

Claims

内燃機関においてクランク軸からのトルク伝達によりカム軸が開閉する動弁のバルブタイミングを調整するバルブタイミング調整装置であって、
駆動側内歯車部を有し、前記クランク軸と連動して回転する駆動側回転体と、
従動側内歯車部を有し、前記カム軸と連動して回転する従動側回転体と、
前記駆動側内歯車部及び前記従動側内歯車部と噛合しつつ遊星運動することにより前記駆動側回転体及び前記従動側回転体の間の相対位相を変化させる遊星歯車と、
を備え、前記駆動側内歯車部及び前記従動側内歯車部の内周側に潤滑液が供給源から供給されるバルブタイミング調整装置において、
前記駆動側回転体及び前記従動側回転体の少なくとも一方である特定回転体は、
前記駆動側内歯車部及び前記従動側内歯車部の少なくとも一方であって前記特定回転体に設けられる特定内歯車部に対し、軸方向に隣接して当該特定内歯車部との間に入隅を形成する壁部と、
前記入隅に向かって開口する開口端とは反対側において閉塞される閉塞端が前記特定内歯車部の歯底よりも径方向の外側に位置すると共に、前記特定内歯車部の回転方向に連続する環状の凹部と、
を有することを特徴とするバルブタイミング調整装置。 A valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine,
A driving side rotating body having a driving side internal gear portion and rotating in conjunction with the crankshaft;
A driven-side rotating body having a driven-side internal gear portion and rotating in conjunction with the camshaft;
A planetary gear that changes a relative phase between the driving side rotating body and the driven side rotating body by performing planetary movement while meshing with the driving side internal gear section and the driven side internal gear section;
A valve timing adjusting device in which a lubricating liquid is supplied from a supply source to the inner peripheral side of the driving side internal gear portion and the driven side internal gear portion;
The specific rotating body that is at least one of the driving side rotating body and the driven side rotating body,
With respect to a specific internal gear portion that is at least one of the driving-side internal gear portion and the driven-side internal gear portion and is provided on the specific rotating body, the corner is adjacent to the specific internal gear portion adjacent in the axial direction. Forming a wall,
A closed end that is closed on the side opposite to the opening end that opens toward the entry corner is positioned radially outside the tooth bottom of the specific internal gear portion, and is continuous in the rotation direction of the specific internal gear portion. An annular recess to
A valve timing adjusting device characterized by comprising:

前記特定内歯車部の内周側において潤滑液は、前記入隅に向かう前記軸方向へ流れることを特徴とする請求項１に記載のバルブタイミング調整装置。 2. The valve timing adjusting device according to claim 1, wherein the lubricating liquid flows in the axial direction toward the entrance corner on the inner peripheral side of the specific internal gear portion.

前記凹部は、前記軸方向に対し傾斜して設けられ、前記軸方向において前記閉塞端が前記開口端よりも前記特定内歯車部とは反対側に位置することを特徴とする請求項１又は２に記載のバルブタイミング調整装置。 The said recessed part is inclined and provided with respect to the said axial direction, The said obstruction | occlusion end is located on the opposite side to the said specific internal gear part rather than the said opening end in the said axial direction. The valve timing adjusting device according to 1.

前記凹部は、
前記開口端を形成すると共に前記軸方向に対し傾斜する傾斜部と、
前記傾斜部に対し屈曲されると共に前記閉塞端を形成する屈曲部と、
を有することを特徴とする請求項３に記載のバルブタイミング調整装置。 The recess is
An inclined portion that forms the open end and is inclined with respect to the axial direction;
A bent portion that is bent with respect to the inclined portion and forms the closed end;
The valve timing adjusting device according to claim 3, wherein

前記屈曲部は、前記軸方向において前記傾斜部よりも前記特定内歯車部とは反対側に前記閉塞端を形成することを特徴とする請求項４に記載のバルブタイミング調整装置。 5. The valve timing adjusting device according to claim 4, wherein the bent portion forms the closed end on a side opposite to the specific internal gear portion with respect to the inclined portion in the axial direction.

前記特定回転体は、前記駆動側回転体及び前記従動側回転体の双方であることを特徴とする請求項１〜５のいずれか一項に記載のバルブタイミング調整装置。 The valve timing adjustment device according to any one of claims 1 to 5, wherein the specific rotator is both the drive-side rotator and the driven-side rotator.

前記凹部よりも潤滑液流れの下流側に配置されて前記駆動側回転体を軸受する軸受を備えることを特徴とする請求項１〜６のいずれか一項に記載のバルブタイミング調整装置。 The valve timing adjusting device according to any one of claims 1 to 6, further comprising a bearing that is disposed downstream of the concave portion in the flow of the lubricating liquid and that bearings the driving-side rotating body.

前記凹部よりも潤滑液流れの下流側に配置されて前記遊星歯車を軸受する軸受を備えることを特徴とする請求項１〜７のいずれか一項に記載のバルブタイミング調整装置。 The valve timing adjusting device according to any one of claims 1 to 7, further comprising a bearing that is disposed downstream of the concave portion in the flow of the lubricating liquid and that bearings the planetary gear.

前記凹部よりも潤滑液流れの下流側に配置されて前記遊星歯車を遊星運動可能に支持する遊星キャリアと、
前記遊星キャリアと嵌合する回転軸体を有し、当該回転軸体により前記遊星キャリアを回転駆動して前記遊星歯車を遊星運動させるアクチュエータと、
を備えることを特徴する請求項１〜８のいずれか一項に記載のバルブタイミング調整装置。 A planet carrier that is arranged downstream of the concave portion in the flow of the lubricating liquid and supports the planetary gear so as to be capable of planetary movement;
An actuator for rotating the planetary carrier by the rotating shaft body and causing the planetary gear to perform a planetary movement, the rotating shaft body fitting with the planetary carrier;
The valve timing adjusting device according to any one of claims 1 to 8, further comprising: