JP5381952B2

JP5381952B2 - Valve timing adjustment device

Info

Publication number: JP5381952B2
Application number: JP2010226873A
Authority: JP
Inventors: 太衛杉浦; 基上濱
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2010-10-06
Filing date: 2010-10-06
Publication date: 2014-01-08
Anticipated expiration: 2030-10-06
Also published as: JP2012082691A

Description

本発明は、内燃機関においてクランク軸からの機関トルクの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 transmission of engine torque from a crankshaft in an internal combustion engine.

従来、クランク軸と連動回転する駆動回転体並びにカム軸と連動回転する従動回転体に遊星歯車を連繋させ、当該遊星歯車の遊星運動によってクランク軸及びカム軸間の相対位相（以下、「機関位相」という）を変化させるバルブタイミング調整装置が、知られている。 Conventionally, a planetary gear is connected to a driving rotating body that rotates in conjunction with a crankshaft and a driven rotating body that rotates in conjunction with a camshaft, and the relative phase between the crankshaft and the camshaft (hereinafter referred to as “engine phase”) by planetary motion of the planetary gear. ) Is known to change the valve timing.

こうした構成のバルブタイミング調整装置として特許文献１に開示の装置では、従動回転体により軸受されると共に機関トルクが伝達される本体部材に対して、遊星歯車と連繋する連繋部材が締結部材により締結されることで、駆動回転体が形成されている。ここで特に、特許文献１に開示の装置では、連繋部材に挿通された締結部材が本体部材に螺合されている。これによれば、締結部材の螺合による連繋部材の歪みが回避され得るので、歪んだ連繋部材と遊星歯車との間で異音や磨耗が発生する事態につき、抑制可能となる。 In the device disclosed in Patent Document 1 as a valve timing adjusting device having such a configuration, a connecting member connected to a planetary gear is fastened by a fastening member to a main body member that is supported by a driven rotor and to which engine torque is transmitted. Thus, a drive rotator is formed. Here, in particular, in the apparatus disclosed in Patent Document 1, a fastening member inserted through the connecting member is screwed into the main body member. According to this, since the distortion of the connecting member due to the screwing of the fastening member can be avoided, it is possible to suppress the occurrence of abnormal noise and wear between the distorted connecting member and the planetary gear.

特開２００９−１６２１０９号公報JP 2009-162109 A

さて、特許文献１に開示の装置では、駆動回転体を構成する筒状の本体部材において、従動回転体により軸受されるジャーナル部が内周部に、また環状のタイミングチェーンを掛け渡されて機関トルクを伝達される伝達部が外周部に、それぞれ形成されている。これにより、トルク伝達時にタイミングチェーンの張力が伝達部に作用する本体部材は、ジャーナル部を軸受する従動回転体により伝達部の内周側にて支持されることで、傾き難くなっているので、当該傾きに起因する異音や磨耗の発生につき、抑制可能となる。 In the apparatus disclosed in Patent Document 1, in a cylindrical main body member constituting a driving rotating body, a journal portion supported by a driven rotating body is stretched over an inner peripheral portion and an annular timing chain is extended to an engine. A transmission portion for transmitting torque is formed on the outer peripheral portion. As a result, the body member on which the tension of the timing chain acts on the transmission part during torque transmission is supported on the inner peripheral side of the transmission part by the driven rotating body bearing the journal part, so that it is difficult to tilt. It is possible to suppress abnormal noise and wear due to the inclination.

しかし、このような構成の下、特許文献１の開示装置では、ジャーナル部及び伝達部の間において締結部材が本体部材に螺合している。そのため、本体部材において締結部材の螺合箇所の内周側に位置するジャーナル部は、当該螺合による歪みに起因して従動回転体との間で異音や磨耗を発生するおそれがあった。また、本体部材において締結部材の螺合箇所の外周側に位置する伝達部は、当該螺合による歪みに起因してタイミングチェーンとの間で異音や磨耗を発生するおそれがあった。 However, with such a configuration, in the disclosed device of Patent Document 1, the fastening member is screwed into the main body member between the journal portion and the transmission portion. For this reason, the journal portion located on the inner peripheral side of the screwed portion of the fastening member in the main body member may generate noise or wear with the driven rotating body due to distortion caused by the screwing. Further, in the main body member, the transmission portion located on the outer peripheral side of the screwing portion of the fastening member may generate noise or wear with the timing chain due to distortion caused by the screwing.

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、バルブタイミング調整装置における異音及び磨耗の抑制効果を高めて、静粛性及び耐久性を確保することにある。 The present invention has been made in view of the above-described problems, and an object of the present invention is to enhance silence noise and wear suppression effect in the valve timing adjusting device and to ensure silence and durability.

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機関トルクの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、クランク軸と連動回転する駆動回転体と、カム軸と連動回転する従動回転体と、駆動回転体及び従動回転体に連繋し、遊星運動することによりクランク軸及びカム軸間の機関位相を変化させる遊星歯車と、を備え、駆動回転体は、従動回転体により軸受されるジャーナル部を、内周部に形成し、環状のトルク伝達部材が掛け渡されることにより機関トルクが伝達される伝達部を、外周部に形成する筒状の本体部材と、遊星歯車に連繋する連繋部材と、連繋部材に挿通されて本体部材に螺合することにより、連繋部材を本体部材に締結する締結部材と、を有するバルブタイミング調整装置において、
本体部材におけるジャーナル部及び伝達部間に、通し孔部が設けられ、本体部材においてジャーナル部及び伝達部間から外れる箇所に、螺子孔部が設けられ、締結部材は、通し孔部に連繋部材側から遊挿されて、螺子孔部に螺合することを特徴とする。 The invention according to claim 1 is a valve timing adjusting device that adjusts the valve timing of a valve that opens and closes a camshaft by transmission of engine torque from a crankshaft in an internal combustion engine, and that rotates in conjunction with the crankshaft A planetary gear that changes the engine phase between the crankshaft and the camshaft by a planetary motion linked to the drive rotator and the driven rotator, and a planetary gear that rotates in conjunction with the camshaft. The rotating body is formed in a cylindrical shape in which a journal portion that is supported by a driven rotating body is formed on an inner peripheral portion, and a transmission portion that transmits an engine torque when an annular torque transmitting member is stretched is formed on an outer peripheral portion. A main body member, a connecting member connected to the planetary gear, and a fastening member inserted into the connecting member and screwed to the main body member to fasten the connecting member to the main body member. In timing control apparatus,
A through hole portion is provided between the journal portion and the transmission portion of the main body member, a screw hole portion is provided at a position where the main body member is separated from between the journal portion and the transmission portion, and the fastening member is connected to the through hole portion on the member side. And is screwed into the screw hole portion.

このように、請求項１に記載の発明において駆動回転体は、連繋部材に挿通された締結部材が本体部材に螺合することにより、形成されることとなる。これによれば、締結部材の螺合による連繋部材の歪みは回避され得るので、歪んだ連繋部材と遊星歯車との間で異音や磨耗が発生する事態につき、抑制可能となる。さらに請求項１に記載の発明では、筒状の本体部材において、従動回転体により軸受されるジャーナル部が内周部に、また環状のトルク伝達部材を掛け渡されて機関トルクを伝達される伝達部が外周部に、それぞれ形成される。これにより、トルク伝達時にトルク伝達部材の張力が伝達部に作用する本体部材は、ジャーナル部を軸受する従動回転体により伝達部の内周側にて支持されることで、傾き難くなるので、当該傾きに起因する異音や磨耗の発生についても、抑制可能となる。 Thus, in the invention described in claim 1, the drive rotator is formed when the fastening member inserted through the connecting member is screwed into the main body member. According to this, since the distortion of the connecting member due to the screwing of the fastening member can be avoided, it is possible to suppress the occurrence of abnormal noise and wear between the distorted connecting member and the planetary gear. Further, in the first aspect of the invention, in the cylindrical body member, the journal portion that is supported by the driven rotating body is passed over the inner peripheral portion and the annular torque transmitting member is transmitted to transmit the engine torque. The part is formed on the outer peripheral part. As a result, the body member on which the tension of the torque transmission member acts on the transmission portion during torque transmission is supported on the inner peripheral side of the transmission portion by the driven rotating body bearing the journal portion, so that it is difficult to tilt. It is also possible to suppress abnormal noise and wear due to the inclination.

しかも、請求項１に記載の発明において締結部材は、本体部材に対して、ジャーナル部及び伝達部間の通し孔部に連繋部材側から遊挿されて、それらの部間から外れた螺子孔部に螺合する。これにより、本体部材において締結部材の螺合箇所の内周側を外れて、同締結部材の遊挿箇所の内周側に位置することとなるジャーナル部は、当該螺合による歪みに起因して従動回転体との間で異音や磨耗を発生する事態につき、抑制可能である。それと共に、本体部材において締結部材の螺合箇所の外周側を外れて、同締結部材の遊挿箇所の外周側に位置することとなる伝達部は、当該螺合による歪みに起因してトルク伝達部材との間で異音や磨耗を発生する事態につき、抑制可能である。 Moreover, in the invention according to claim 1, the fastening member is loosely inserted into the through hole portion between the journal portion and the transmission portion from the connecting member side with respect to the main body member, and is removed from between these portions. Threaded onto. Thereby, in the main body member, the journal portion that is located on the inner peripheral side of the loose insertion portion of the fastening member and is located on the inner peripheral side of the loose insertion portion of the fastening member is caused by distortion due to the screw engagement. It is possible to suppress the occurrence of abnormal noise and wear with the driven rotor. At the same time, the transmission part that is located on the outer peripheral side of the loose insertion portion of the fastening member and that is located on the outer peripheral side of the loose insertion portion of the fastening member in the main body member transmits torque due to distortion caused by the screw engagement. It is possible to suppress the occurrence of abnormal noise and wear with the member.

以上説明したことから、請求項１に記載の発明は、異音及び磨耗の抑制効果の高いバルブタイミング調整装置となり得る。したがって、バルブタイミング調整装置の静粛性及び耐久性を確保することができる。 As described above, the invention according to claim 1 can be a valve timing adjusting device having a high effect of suppressing abnormal noise and wear. Therefore, the silence and durability of the valve timing adjusting device can be ensured.

請求項２に記載の発明によると、本体部材において通し孔部は、ジャーナル部及び伝達部が軸方向に沿って重なる箇所に、設けられる。この発明において、軸方向に沿って伝達部と重なるジャーナル部は、トルク伝達部材の張力を伝達部の内周側にて径方向に受けることになるので、歪みが生じている場合には、従動回転体との間で異音や磨耗を発生し易くなる。しかし、そうしたジャーナル部及び伝達部の重なり箇所の通し孔部に遊挿される締結部材は、当該重なり箇所を外れた螺子孔部に螺合することになるので、ジャーナル部の歪みを招き難い。したがって、ジャーナル部の歪みに起因する異音及び磨耗の発生に対して、抑制効果を高めることができるのである。 According to invention of Claim 2, a through-hole part is provided in the location where a journal part and a transmission part overlap along an axial direction in a main body member. In this invention, the journal portion that overlaps the transmission portion along the axial direction receives the tension of the torque transmission member in the radial direction on the inner peripheral side of the transmission portion. Abnormal noise and wear are likely to occur between the rotating bodies. However, since the fastening member loosely inserted into the through hole portion at the overlapping portion of the journal portion and the transmission portion is screwed into the screw hole portion outside the overlapping portion, it is difficult to cause distortion of the journal portion. Therefore, it is possible to enhance the suppression effect against the occurrence of abnormal noise and wear due to the distortion of the journal portion.

請求項３に記載の発明によると、本体部材において通し孔部は、ジャーナル部の外周側の軸方向全域及び伝達部の内周側の軸方向全域を包含する箇所に、設けられる。この発明の本体部材において通し孔部は、ジャーナル部の外周側の軸方向全域及び伝達部の内周側の軸方向全域を包含する箇所に設けられることで、それら部の双方と軸方向に沿って重なるだけでなく、それら部の一方のみと軸方向に沿って重なることとなる。こうした通し孔部に締結部材が遊挿されることによれば、同締結部材が本体部材の螺子孔部に螺合することによる歪みを、ジャーナル部及び伝達部の双方において確実に低減し得る。したがって、ジャーナル部の歪みに起因する異音や磨耗の発生に対しても、伝達部の歪みに起因する異音や磨耗の発生に対しても、抑制効果を高めることができる。 According to the third aspect of the present invention, in the main body member, the through hole portion is provided at a location including the entire axial direction region on the outer peripheral side of the journal portion and the entire axial direction region on the inner peripheral side of the transmission portion. In the main body member of the present invention, the through-hole portion is provided in a location including the entire axial direction region on the outer peripheral side of the journal portion and the entire axial direction region on the inner peripheral side of the transmission portion. In addition to overlapping, only one of these portions overlaps along the axial direction. When the fastening member is loosely inserted into such a through hole portion, distortion due to the fastening member screwing into the screw hole portion of the main body member can be surely reduced in both the journal portion and the transmission portion. Therefore, it is possible to enhance the effect of suppressing abnormal noise and wear due to distortion of the journal portion as well as abnormal noise and wear due to distortion of the transmission portion.

請求項４に記載の発明によると、筒状の本体部材は、連繋部材が圧入される圧入部を、内周部のうちジャーナル部と隣接する箇所に形成し、本体部材において通し孔部は、ジャーナル部及び伝達部間から圧入部の外周側に跨って、設けられる。この発明では、筒状の本体部材の内周部においてジャーナル部と隣接する圧入部は、連繋部材の圧入により歪む事態につき、懸念される。しかし、ジャーナル部及び伝達部間から圧入部の外周側に跨る通し孔部に遊挿される締結部材は、当該圧入部の外周側から外れた螺子孔部に螺合することになるので、当該圧入部の歪みが螺子孔部への螺合状態に影響し難い。これによれば、本体部材及び連繋部材の締結部材による締結強度につき、ばらつきが抑制され得るので、バルブタイミング調整装置の耐久性の向上に貢献可能である。 According to the invention of claim 4, the cylindrical main body member is formed with a press-fit portion into which the connecting member is press-fitted at a location adjacent to the journal portion of the inner peripheral portion, and the through hole portion in the main body member is It is provided across the outer peripheral side of the press-fitting part from between the journal part and the transmission part. In the present invention, there is a concern about the situation where the press-fitting part adjacent to the journal part in the inner peripheral part of the cylindrical body member is distorted by the press-fitting of the connecting member. However, since the fastening member loosely inserted into the through hole extending over the outer peripheral side of the press-fitting part from between the journal part and the transmission part is screwed into the screw hole part removed from the outer peripheral side of the press-fitting part. The distortion of the portion hardly affects the screwed state to the screw hole. According to this, since the variation in the fastening strength of the fastening member of the main body member and the connecting member can be suppressed, it is possible to contribute to the improvement of the durability of the valve timing adjusting device.

請求項５に記載の発明によると、伝達部は、金属製の本体部材に対して焼き入れ処理が施されてなる。この発明において、金属製の本体部材に対して焼き入れ処理が施されてなる伝達部は、剛性が高くなる一方で靭性が低くなる傾向にあるため、歪みの発生により割れる事態が懸念される。しかし、締結部材の螺合箇所の外周側を外れて同締結部材の遊挿箇所の外周側に位置することとなる伝達部は、当該螺合による歪みに起因した割れを抑制され得るので、バルブタイミング調整装置の耐久性の向上に貢献可能である。 According to the invention described in claim 5, the transmission part is formed by quenching the metal body member. In this invention, since the transmission part formed by quenching the metal main body member tends to have high rigidity and low toughness, there is a concern that the crack may occur due to the occurrence of distortion. However, since the transmission part that is located on the outer peripheral side of the loose insertion portion of the fastening member by removing the outer peripheral side of the fastening member's screwing portion can be prevented from cracking due to distortion due to the screwing, the valve This can contribute to improving the durability of the timing adjustment device.

本発明の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 one 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の遊星歯車機構の要部を拡大して示す断面図である。It is sectional drawing which expands and shows the principal part of the planetary gear mechanism of FIG.

以下、本発明の一実施形態を図面に基づいて説明する。図１は、本発明の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、クランク軸及びカム軸２間の機関位相に応じて当該吸気弁のバルブタイミングを調整する。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a valve timing adjusting apparatus 1 according to an 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 engine torque. The valve timing adjusting device 1 includes a crankshaft and a camshaft. The valve timing of the intake valve is adjusted according to the engine phase between the two.

（基本構成）
以下、バルブタイミング調整装置１の基本構成を説明する。図１に示すようにバルブタイミング調整装置１は、アクチュエータ３、通電制御回路部４及び遊星歯車機構５等を組み合わせてなる。 (Basic configuration)
Hereinafter, a basic configuration of the valve timing adjusting device 1 will be described. As shown in FIG. 1, the valve timing adjusting device 1 is formed by combining an actuator 3, an energization control circuit unit 4, a planetary gear mechanism 5, and the like.

アクチュエータ３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６と、当該ケース６により正逆回転自在に支持される制御軸７とを有している。通電制御回路部４は、例えば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６の外部及び／又は内部に配置されてアクチュエータ３と電気的に接続されている。通電制御回路部４は、機関位相を内燃機関の運転状態に応じた位相に調整するよう、アクチュエータ３への通電によって制御軸７の回転状態を制御する。遊星歯車機構５は、駆動回転体１０、従動回転体２０、遊星キャリア４０及び遊星歯車５０を備えている。 The actuator 3 is an electric motor such as a brushless motor, for example, and includes a case 6 fixed to a fixed node of the internal combustion engine and a control shaft 7 supported by the case 6 so as to be rotatable forward and backward. The energization control circuit unit 4 includes, for example, a drive driver and a control microcomputer thereof, and is disposed outside and / or inside the case 6 and is electrically connected to the actuator 3. The energization control circuit unit 4 controls the rotation state of the control shaft 7 by energizing the actuator 3 so as to adjust the engine phase to a phase corresponding to the operating state of the internal combustion engine. The planetary gear mechanism 5 includes a drive rotator 10, a driven rotator 20, a planet carrier 40, and a planetary gear 50.

図１〜３に示すように全体として筒状の駆動回転体１０は、遊星歯車機構５の他の構成要素２０，４０，５０を内部に収容している。駆動回転体１０は、本体部材１１に対して連繋部材１２及びカバー部材１３を、複数の締結部材１４により螺子留めしてなる。 As shown in FIGS. 1 to 3, the overall cylindrical drive rotor 10 accommodates the other constituent elements 20, 40, and 50 inside the planetary gear mechanism 5. The drive rotating body 10 is formed by screwing a connecting member 12 and a cover member 13 to a main body member 11 with a plurality of fastening members 14.

有底円筒状の本体部材１１は、従動回転体２０により軸受されるジャーナル部１５と、連繋部材１２が圧入される圧入部１６とを、内周部のうち互いに軸方向に隣接する箇所に形成している。また、本体部材１１は、スプロケット歯１７ａが駆動回転体１０の回転方向に複数並んでなる伝達部１７を、外周部に形成している。伝達部１７は、それらのスプロケット歯１７ａとクランク軸の複数のスプロケット歯との間でタイミングチェーン８が「環状のトルク伝達部材」として掛け渡されることにより、クランク軸と連繋する。かかる連繋により、クランク軸から出力される機関トルクがチェーン８を通じて伝達部１７に伝達されると、駆動回転体１０が当該クランク軸と連動して回転する。このときの駆動回転体１０の回転方向は、常に一定方向（図２の反時計方向且つ図３の時計方向）となる。 The bottomed cylindrical main body member 11 is formed with a journal portion 15 that is supported by the driven rotor 20 and a press-fit portion 16 into which the connecting member 12 is press-fitted at locations adjacent to each other in the axial direction on the inner peripheral portion. doing. Further, the main body member 11 has a transmission portion 17 in which a plurality of sprocket teeth 17 a are arranged in the rotation direction of the drive rotating body 10 on the outer peripheral portion. The transmission portion 17 is linked to the crankshaft by the timing chain 8 being spanned as an “annular torque transmission member” between the sprocket teeth 17a and the plurality of sprocket teeth of the crankshaft. With this connection, when the engine torque output from the crankshaft is transmitted to the transmission portion 17 through the chain 8, the drive rotator 10 rotates in conjunction with the crankshaft. At this time, the rotation direction of the drive rotor 10 is always a constant direction (counterclockwise in FIG. 2 and clockwise in FIG. 3).

図１，２に示すように円環板状の連繋部材１２は、圧入部１６の円筒面状内周面に圧入されて本体部材１１に同軸上に締結されており、内周部に駆動側内歯車部１８を形成している。駆動側内歯車部１８は、遊星歯車５０と歯車連繋可能に、歯先円を歯底円の内周側に有している。連繋部材１２と同軸上に配置される円環状のカバー部材１３は、本体部材１１に対して当該連繋部材１２を軸方向に挟んで締結されている。 As shown in FIGS. 1 and 2, the annular plate-like connecting member 12 is press-fitted into the cylindrical inner peripheral surface of the press-fit portion 16 and is coaxially fastened to the main body member 11, and is connected to the inner peripheral portion on the drive side. An internal gear portion 18 is formed. The drive-side internal gear portion 18 has a tip circle on the inner peripheral side of the root circle so that the planetary gear 50 can be gear-connected. An annular cover member 13 arranged coaxially with the connecting member 12 is fastened to the main body member 11 with the connecting member 12 sandwiched in the axial direction.

図１，３に示すように有底円筒状の従動回転体２０は、ジャーナル部１５の円筒面状内周面に嵌合することにより本体部材１１を軸受する軸受部２１を、外周部に形成している。また、従動回転体２０は、カム軸２に同軸上に連結される連結部２２を、底部に形成している。かかる要素２２，２同士の連結によって従動回転体２０は、カム軸２と連動して回転可能且つ駆動回転体１０に対して相対回転可能となっている。ここで、従動回転体２０の回転方向は、駆動回転体１０と同一方向（図３の時計方向）に設定されている。 As shown in FIGS. 1 and 3, the bottomed cylindrical follower rotating body 20 is formed on the outer peripheral portion with a bearing portion 21 for bearing the main body member 11 by being fitted to the cylindrical inner peripheral surface of the journal portion 15. doing. Further, the driven rotor 20 has a connecting portion 22 that is coaxially connected to the camshaft 2 at the bottom. The driven rotor 20 can rotate in conjunction with the camshaft 2 and can rotate relative to the drive rotor 10 by connecting the elements 22 and 2 together. Here, the rotation direction of the driven rotator 20 is set in the same direction as the drive rotator 10 (clockwise in FIG. 3).

さらに従動回転体２０は、内周部に従動側内歯車部２４を形成している。従動側内歯車部２４は、遊星歯車５０と歯車連繋可能に、歯先円を歯底円の内周側に有している。従動側内歯車部２４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２４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２４は、駆動側内歯車部１８から軸方向にずれて配置されている。 Further, the driven rotor 20 forms a driven side internal gear portion 24 on the inner peripheral portion. The driven side internal gear portion 24 has a tip circle on the inner peripheral side of the root circle so as to be gear-coupled to the planetary gear 50. The inner diameter of the driven side internal gear portion 24 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 24 is set smaller than the number of teeth of the drive side internal gear portion 18. . The driven side internal gear portion 24 is arranged so as to be shifted from the drive side internal gear portion 18 in the axial direction.

図１，２に示すように円筒状の遊星キャリア４０は、内周部に連結部４１を形成している。連結部４１は、回転体１０，２０及び制御軸７と同心の円筒面状内周面に、制御軸７の継手部４３と嵌合する嵌合溝４２が開口形成されてなる。かかる要素４３，４２同士の嵌合によって遊星キャリア４０は、制御軸７と一体に回転可能且つ駆動側内歯車部１８に対して相対回転可能となっている。 As shown in FIGS. 1 and 2, the cylindrical planetary carrier 40 has a connecting portion 41 formed on the inner peripheral portion. The coupling portion 41 is formed by opening a fitting groove 42 that fits with the joint portion 43 of the control shaft 7 on the inner circumferential surface of the cylindrical surface concentric with the rotating bodies 10 and 20 and the control shaft 7. The planet carrier 40 can rotate integrally with the control shaft 7 and can rotate relative to the drive-side internal gear portion 18 by fitting the elements 43 and 42 together.

さらに遊星キャリア４０は、図１〜３に示すように、外周部に偏心部４４を形成している。偏心部４４は、回転体１０，２０及び制御軸７とは偏心する円筒面状外周面に対して、遊星ベアリング４５を挟んで連繋する遊星歯車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が偏心部４４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運動をいう。したがって、制御軸７と共に遊星キャリア４０が遊星歯車５０の公転方向へ回転するときには、当該遊星歯車５０が遊星運動することになる。 Further, as shown in FIGS. 1 to 3, the planet carrier 40 has an eccentric portion 44 formed on the outer peripheral portion. The eccentric portion 44 supports the planetary gear 50 that is connected to the cylindrical outer peripheral surface that is eccentric from the rotating bodies 10 and 20 and the control shaft 7 with the planetary bearing 45 interposed therebetween so as to be capable of planetary movement. Here, the planetary motion refers to a motion in which the planetary gear 50 revolves around the eccentric center line of the eccentric portion 44 and revolves in the rotation direction of the planetary carrier 40. Therefore, when the planetary carrier 40 rotates in the revolving direction of the planetary gear 50 together with the control shaft 7, the planetary gear 50 makes a planetary motion.

段付円筒状の遊星歯車５０は、駆動側外歯車部５２と従動側外歯車部５４とをそれぞれ、大径外周部と小径外周部とに形成している。駆動側内歯車部１８の内周側に偏心配置される駆動側外歯車部５２は、歯底円の外周側に歯先円を有することにより、当該駆動側内歯車部１８と噛合している。駆動側外歯車部５２から軸方向にずれて従動側内歯車部２４の内周側に偏心配置される従動側外歯車部５４は、歯底円の外周側に歯先円を有することにより、当該従動側内歯車部２４と噛合している。従動側外歯車部５４の外径は駆動側外歯車部５２の外径よりも小さく設定され、またそれら従動側外歯車部５４及び駆動側外歯車部５２の歯数は、それぞれ従動側内歯車部２４及び駆動側内歯車部１８の歯数よりも同数ずつ少なく設定されている。 The stepped cylindrical planetary gear 50 has a driving-side external gear portion 52 and a driven-side external gear portion 54 formed on a large-diameter outer peripheral portion and a small-diameter outer peripheral portion, respectively. The drive-side external gear portion 52 that is eccentrically arranged on the inner peripheral side of the drive-side internal gear portion 18 meshes with the drive-side internal gear portion 18 by having a tooth tip circle on the outer peripheral side of the root circle. . The driven-side external gear portion 54 that is offset in the axial direction from the drive-side external gear portion 52 and is eccentrically disposed on the inner peripheral side of the driven-side internal gear portion 24 has a tooth tip circle on the outer peripheral side of the root circle. The driven side internal gear portion 24 meshes with the driven side internal gear portion 24. The outer diameter of the driven-side external gear portion 54 is set smaller than the outer diameter of the driving-side external gear portion 52, and the number of teeth of the driven-side external gear portion 54 and the driving-side external gear portion 52 is respectively the driven-side internal gear. The number of teeth is set to be the same as the number of teeth of the portion 24 and the drive side internal gear portion 18.

このようにして回転体１０，２０間を歯車連繋してなる遊星歯車機構５は、制御軸７の回転状態に応じた機関位相を実現して、バルブタイミングを調整する。具体的には、制御軸７が駆動回転体１０と同速に回転することで、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が遊星運動せずに回転体１０，２０と連れ回りする。その結果、機関位相は変化しないので、バルブタイミングが保持される。 Thus, the planetary gear mechanism 5 in which the rotating bodies 10 and 20 are geared together realizes the engine phase according to the rotation state of the control shaft 7 and adjusts the valve timing. Specifically, when the control shaft 7 rotates at the same speed as the drive rotor 10, the planetary gear 50 rotates without planetary motion when the planetary carrier 40 does not rotate relative to the drive-side internal gear unit 18. Along with the body 10,20. As a result, since the engine phase does not change, the valve timing is maintained.

制御軸７が駆動回転体１０よりも高速に回転することで、遊星キャリア４０が駆動側内歯車部１８に対する進角側へ相対回転するときには、遊星歯車５０の遊星運動によって従動回転体２０が駆動回転体１０に対する進角側へ相対回転する。その結果、機関位相は進角側へと変化するので、バルブタイミングが進角することになる。一方、制御軸７が駆動回転体１０よりも低速に回転する又は駆動回転体１０とは逆に回転することで、遊星キャリア４０が駆動側内歯車部１８に対する遅角側へ相対回転するときには、遊星歯車５０の遊星運動によって従動回転体２０が駆動回転体１０に対する遅角側へ相対回転する。その結果、機関位相は遅角側へと変化するので、バルブタイミングが遅角することになる。 When the control shaft 7 rotates at a higher speed than the drive rotator 10, the planetary carrier 40 rotates relative to the advance side with respect to the drive-side internal gear portion 18, so that the driven rotator 20 is driven by the planetary motion of the planetary gear 50. Relative rotation with respect to the rotating body 10 toward the advance side. As a result, the engine phase changes to the advance side, and the valve timing advances. On the other hand, when the planetary carrier 40 rotates relative to the drive-side internal gear portion 18 relative to the retard side by rotating the control shaft 7 at a lower speed than the drive rotator 10 or rotating in the opposite direction to the drive rotator 10, Due to the planetary movement of the planetary gear 50, the driven rotator 20 rotates relative to the drive rotator 10 toward the retard side. As a result, the engine phase changes to the retard side, so that the valve timing is retarded.

（特徴構成）
以下、バルブタイミング調整装置１の特徴構成を説明する。図１〜３に示すように、駆動回転体１０において回転方向に間隔をあけた複数個所（本実施形態では、四箇所）には、金属製の構成部材１１，１２，１３を軸方向に沿って貫通する締結孔１００が設けられ、それら各締結孔１００には、金属ボルトからなる締結部材１４が個別に挿入されている。尚、締結孔１００及び締結部材１４の各組の構成は、配設位置以外は互いに実質同一であるので、以下では、図４に示す一組の構成について詳細を説明する。 (Feature configuration)
Hereinafter, a characteristic configuration of the valve timing adjusting device 1 will be described. As shown in FIGS. 1 to 3, the metal component members 11, 12, and 13 are arranged in the axial direction at a plurality of locations (four locations in the present embodiment) spaced apart in the rotational direction in the drive rotator 10. Fastening holes 100 penetrating therethrough are provided, and fastening members 14 made of metal bolts are individually inserted into the fastening holes 100. In addition, since the structure of each set of the fastening hole 100 and the fastening member 14 is substantially the same except for the arrangement position, the details of the set of structures shown in FIG. 4 will be described below.

締結孔１００において、カバー部材１３及び連繋部材１２がそれぞれ形成する挿通孔部１１３，１１２には、締結部材１４の軸部１１４ａのうち螺子部１１４ｂの設けられていない円筒部１１４ｃが、挿通されている。ここで各挿通孔部１１３，１１２は、円筒部１１４ｃの外径よりも大きな内径をもって軸方向にストレートに延伸する円筒孔状に、それぞれ形成されている。これにより円筒部１１４ｃは、各挿通孔部１１３，１１２を非螺合状態で貫通して、同じ締結部材１４の頭部１１４ｄをカバー部材１３の軸方向端面に当接させている。尚、本実施形態において円筒部１１４ｃの外径は、螺子部１１４ｂの螺子山の径よりも小さく設定されており、当該外径に応じて各挿通孔部１１３，１１２の内径が設定される。 In the fastening hole 100, the cylindrical portion 114 c that is not provided with the screw portion 114 b of the shaft portion 114 a of the fastening member 14 is inserted into the insertion hole portions 113 and 112 formed by the cover member 13 and the connecting member 12, respectively. Yes. Here, each of the insertion hole portions 113 and 112 is formed in a cylindrical hole shape having an inner diameter larger than the outer diameter of the cylindrical portion 114c and extending straight in the axial direction. Thereby, the cylindrical portion 114 c penetrates the insertion hole portions 113 and 112 in a non-threaded state, and the head portion 114 d of the same fastening member 14 is brought into contact with the axial end surface of the cover member 13. In the present embodiment, the outer diameter of the cylindrical portion 114c is set smaller than the diameter of the screw thread of the screw portion 114b, and the inner diameters of the insertion hole portions 113 and 112 are set according to the outer diameter.

締結孔１００において、挿通孔部１１２との接続箇所に本体部材１１が形成する通し孔部１１１ａには、締結部材１４の軸部１１４ａのうち雄螺子状の螺子部１１４ｂの一部が、挿通されている。ここで通し孔部１１１ａは、螺子部１１４ｂの螺子山の径よりも大きな内径をもって軸方向にストレートに延伸する円筒孔状に、形成されている。これにより螺子部１１４ｂは、連繋部材１２側から通し孔部１１１ａに遊挿されて、当該通し孔部１１１ａを非螺合状態で貫通している。尚、通し孔部１１１ａは、螺子部１１４ｂの螺子山との間に径方向のクリアランス１１１ｃを確保して遊挿状態を維持可能な寸法範囲に、内径設定されていればよく、例えば当該寸法範囲内で挿通孔部１１３，１１２の内径未満となるように、内径設定される。尚、図４においてクリアランス１１１ｃは、説明の理解を容易にするために、誇張して大きく描かれている。 In the fastening hole 100, a part of the male screw-like screw part 114 b of the shaft part 114 a of the fastening member 14 is inserted into the through-hole part 111 a formed by the main body member 11 at a connection position with the insertion hole part 112. ing. Here, the through-hole portion 111a is formed in a cylindrical hole shape that extends straight in the axial direction with an inner diameter larger than the diameter of the screw thread of the screw portion 114b. Thereby, the screw part 114b is loosely inserted into the through hole part 111a from the connecting member 12 side, and penetrates the through hole part 111a in a non-screwed state. In addition, the through-hole part 111a should just be set to the internal diameter within the dimension range which can ensure the radial clearance 111c between the thread parts of the screw part 114b, and can maintain a loose insertion state, for example, the said dimension range The inner diameter is set to be smaller than the inner diameters of the insertion hole portions 113 and 112. In FIG. 4, the clearance 111c is exaggerated and drawn to facilitate understanding of the description.

またここで、本実施形態の通し孔部１１１ａは、本体部材１１における特定箇所、具体的には、ジャーナル部１５の外周側の軸方向全域Ｊと圧入部１６の外周側の軸方向全域Ｐと伝達部１７の内周側の軸方向全域Ｔとのいずれも包含する箇所に、形成されている。これにより通し孔部１１１ａは、ジャーナル部１５と伝達部１７とが軸方向に沿って重なる箇所に設けられ、それら部１５，１７の間から圧入部１６の外周側に跨って軸方向に延伸する形となっている。 In addition, here, the through-hole portion 111a of the present embodiment includes a specific portion in the main body member 11, specifically, an axial region J on the outer peripheral side of the journal portion 15 and an axial region P on the outer peripheral side of the press-fit portion 16. It is formed at a location including both the entire axial direction T on the inner peripheral side of the transmission portion 17. Thereby, the through-hole part 111a is provided in the location where the journal part 15 and the transmission part 17 overlap along the axial direction, and extends in the axial direction across the outer peripheral side of the press-fit part 16 from between these parts 15 and 17. It is in shape.

締結孔１００において、通し孔部１１１ａとの接続箇所に本体部材１１が形成する雌螺子状の螺子孔部１１１ｂには、締結部材１４の軸部１１４ａのうち当該通し孔部１１１ａ側から突き出た螺子部１１４ｂの残部が、螺合している。これにより、螺子部１１４ｂの螺着された本体部材１１は、頭部１１４ｄとの間に連繋部材１２及びカバー部材１３を挟持する状態で、それら部材１２，１３と締結されている。 In the fastening hole 100, a female screw-like screw hole 111 b formed by the main body member 11 at a connection position with the through-hole part 111 a has a screw protruding from the through-hole part 111 a side of the shaft part 114 a of the fastening member 14. The remaining part of the part 114b is screwed. Thereby, the main body member 11 to which the screw portion 114b is screwed is fastened to the members 12 and 13 in a state in which the connecting member 12 and the cover member 13 are sandwiched between the head portion 114d.

ここで、本実施形態の螺子孔部１１１ｂは、本体部材１１における特定箇所、具体的には、ジャーナル部１５の外周側の軸方向全域Ｊと圧入部１６の外周側の軸方向全域Ｐと伝達部１７の内周側の軸方向全域Ｔとのいずれからも外れる箇所に、形成されている。これにより螺子孔部１１１ｂは、ジャーナル部１５及び伝達部１７が軸方向に沿って重なる箇所には設けられず、それら部１５，１７の間から外れると共に、圧入部１６の外周側からも外れる形となっている。 Here, the screw hole portion 111b of the present embodiment transmits a specific portion in the main body member 11, specifically, the axial region J on the outer peripheral side of the journal portion 15 and the axial region P on the outer peripheral side of the press-fit portion 16. It is formed at a location deviating from any of the entire axial direction T on the inner peripheral side of the portion 17. As a result, the screw hole portion 111b is not provided at a location where the journal portion 15 and the transmission portion 17 overlap in the axial direction, and is removed from between the portions 15 and 17 and also from the outer peripheral side of the press-fit portion 16. It has become.

ここまで説明したように、バルブタイミング調整装置１において駆動回転体１０は、カバー部材１３及び連繋部材１２に挿通された締結部材１４が本体部材１１に螺合することにより、形成されている。これによれば、締結部材１４の螺合による連繋部材１２の歪みは回避され得るので、歪んだ連繋部材１２と遊星歯車５０との間で異音や磨耗が発生する事態につき、抑制可能となる。さらに、バルブタイミング調整装置１において円筒状の本体部材１１では、従動回転体２０の軸受部２１により軸受されるジャーナル部１５が内周部に、また環状のタイミングチェーン８を掛け渡されて機関トルクを伝達される伝達部１７が外周部に、それぞれ形成されている。これにより、トルク伝達時にチェーン８の張力が伝達部１７に作用する本体部材１１は、ジャーナル部１５を軸受する従動回転体２０により伝達部１７の内周側にて支持されることで、傾き難くなるので、当該傾きに起因する異音や磨耗の発生についても、抑制可能となる。 As described so far, in the valve timing adjusting device 1, the drive rotator 10 is formed by the fastening member 14 inserted through the cover member 13 and the connecting member 12 being screwed into the main body member 11. According to this, since the distortion of the linking member 12 due to the screwing of the fastening member 14 can be avoided, it is possible to suppress the occurrence of abnormal noise and wear between the distorted linking member 12 and the planetary gear 50. . Further, in the valve timing adjusting device 1, in the cylindrical main body member 11, the journal portion 15, which is supported by the bearing portion 21 of the driven rotor 20, is wound around the inner peripheral portion and the annular timing chain 8 is laid over the engine torque. Are transmitted to the outer peripheral portion. As a result, the body member 11 in which the tension of the chain 8 acts on the transmission portion 17 during torque transmission is supported on the inner peripheral side of the transmission portion 17 by the driven rotating body 20 bearing the journal portion 15, so that it is difficult to tilt. Therefore, it is possible to suppress the occurrence of abnormal noise and wear due to the inclination.

しかも、バルブタイミング調整装置１において締結部材１４は、本体部材１１に対して、ジャーナル部１５及び伝達部１７間の通し孔部１１１ａに連繋部材１２側から遊挿されて、それらの部１５，１７間から外れた螺子孔部１１１ｂに螺合している。これにより、本体部材１１において締結部材１４の螺合箇所の外周側を外れて、同締結部材１４の遊挿箇所の外周側に位置している伝達部１７は、当該螺合による歪みに起因してタイミングチェーン８との間で異音や磨耗を発生する事態につき、抑制可能である。それと共に、本体部材１１において締結部材１４の螺合箇所の内周側を外れて、同締結部材１４の遊挿箇所の内周側に位置しているジャーナル部１５は、当該螺合による歪みに起因して従動回転体２０との間で異音や磨耗を発生する事態につき、抑制可能となる。ここで特に、軸方向に沿って伝達部１７と重なるジャーナル部１５は、チェーン８の張力を伝達部１７の内周側にて径方向に受けるため、歪みに起因する異音や磨耗の発生が懸念されるが、そうした重なり箇所では締結部材１４が遊挿状態にあるため、当該歪み自体を招き難い。また特に、ジャーナル部１５の外周側の軸方向全域Ｊ及び伝達部１７の内周側の軸方向全域Ｔを包含する箇所では、締結部材１４の遊挿される通し孔部１１１ａが、それら部１５，１７の少なくとも一方に対して軸方向に沿って重なることになる。その結果として締結部材１４は、ジャーナル部１５の外周側からも伝達部１７の内周側からも外れた螺子孔部１１１ｂに、螺合されているので、当該螺合よる各部１５，１７の歪みを確実に低減して、異音及び磨耗の抑制効果を高めることができるのである。 In addition, in the valve timing adjusting device 1, the fastening member 14 is loosely inserted into the main body member 11 from the connecting member 12 side into the through hole portion 111 a between the journal portion 15 and the transmission portion 17, and the portions 15, 17. It is screwed into the screw hole 111b that is out of the space. As a result, the transmission portion 17 located on the outer peripheral side of the loose insertion portion of the fastening member 14 from the outer peripheral side of the fastening member 14 in the main body member 11 is caused by distortion due to the screw engagement. Therefore, it is possible to suppress the occurrence of abnormal noise and wear with the timing chain 8. At the same time, the journal portion 15 located on the inner peripheral side of the loose insertion position of the fastening member 14 is removed from the inner peripheral side of the screwing position of the fastening member 14 in the main body member 11, and the distortion due to the screwing is caused. Therefore, it is possible to suppress the occurrence of abnormal noise and wear with the driven rotor 20. Here, in particular, since the journal portion 15 that overlaps the transmission portion 17 along the axial direction receives the tension of the chain 8 in the radial direction on the inner peripheral side of the transmission portion 17, abnormal noise and wear due to distortion are generated. Although it is a concern, since the fastening member 14 is in the loosely inserted state at such an overlapping portion, it is difficult to cause the distortion itself. In particular, in a portion including the entire axial direction J on the outer peripheral side of the journal portion 15 and the entire axial direction T on the inner peripheral side of the transmission portion 17, the through-hole portion 111 a into which the fastening member 14 is loosely inserted is the portions 15, It overlaps along the axial direction with respect to at least one of 17. As a result, the fastening member 14 is screwed into the screw hole portion 111b which is disengaged from both the outer peripheral side of the journal portion 15 and the inner peripheral side of the transmission portion 17, and therefore, the distortion of the respective portions 15 and 17 due to the screwing. Therefore, the effect of suppressing abnormal noise and wear can be enhanced.

以上より、バルブタイミング調整装置１では、異音及び磨耗の抑制効果が高められ得て、静粛性及び耐久性が確保されることになる。但し、バルブタイミング調整装置１では、円筒状の本体部材１１の内周部においてジャーナル部１５と軸方向に隣接する圧入部１６については、連繋部材１２の圧入による歪みが懸念される。しかし、締結部材１４は、圧入部１６の外周側に形成される通し孔部１１１ａに遊挿されて、当該外周側から外れる螺子孔部１１１ｂに螺合しているので、圧入部１６の歪みが螺子孔部１１１ｂへの螺合状態（例えば軸力や内部応力等）に影響し難い。これによれば、部材１１〜１３の締結部材１４による締結強度につき、ばらつきが抑制され得るので、バルブタイミング調整装置１の耐久性の向上に貢献可能である。 From the above, in the valve timing adjusting device 1, the effect of suppressing abnormal noise and wear can be enhanced, and silence and durability are ensured. However, in the valve timing adjusting device 1, there is a concern about the distortion due to the press-fitting of the connecting member 12 in the press-fitting portion 16 that is axially adjacent to the journal portion 15 in the inner peripheral portion of the cylindrical main body member 11. However, since the fastening member 14 is loosely inserted into the through-hole portion 111a formed on the outer peripheral side of the press-fit portion 16 and is screwed into the screw hole portion 111b that is disengaged from the outer peripheral side, the press-fit portion 16 is distorted. It is difficult to influence the screwed state (for example, axial force or internal stress) to the screw hole 111b. According to this, since the dispersion | variation can be suppressed about the fastening strength by the fastening member 14 of the members 11-13, it can contribute to the improvement of durability of the valve timing adjustment apparatus 1. FIG.

また、バルブタイミング調整装置１では、金属製の本体部材１１のうち伝達部１７に対して剛性を高めるための高周波焼き入れ処理を施すような場合、靭性が低くなる傾向にあるため、当該焼き入れ処理後の伝達部１７は、歪みに起因する割れが生じ易くなる。しかし、締結部材１４の螺合箇所の外周側を外れて同締結部材１４の遊挿箇所の外周側に位置している伝達部１７は、焼き入れ処理後にあっても、当該螺合による歪みに起因した割れを抑制され得るので、バルブタイミング調整装置１の耐久性の向上に貢献可能である。 Further, in the valve timing adjusting device 1, when the induction hardening process for increasing the rigidity of the transmission part 17 in the metal main body member 11 is performed, the toughness tends to be lowered, and thus the quenching is performed. The transmission unit 17 after processing is likely to be cracked due to distortion. However, the transmission portion 17 located on the outer peripheral side of the loose insertion portion of the fastening member 14 outside the outer peripheral side of the screwing portion of the fastening member 14 is distorted by the screwing even after the quenching process. Since the resulting cracks can be suppressed, it is possible to contribute to improving the durability of the valve timing adjusting device 1.

（他の実施形態）
以上、本発明の一実施形態について説明したが、本発明は、当該実施形態に限定して解釈されるものではなく、本発明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 one embodiment of the present invention has been described above, the present invention is not construed as being limited to the embodiment, and can be applied to various embodiments without departing from the gist of the present invention. it can.

具体的には、通し孔部１１１ａ及び螺子孔部１１１ｂを有する締結孔１００の配設数は、バルブタイミング調整装置１の仕様に応じて適宜設定してもよい。また、通し孔部１１１ａは、ジャーナル部１５及び伝達部１７が軸方向に沿って重なる箇所のみに、即ち図４の領域Ｊ，Ｔが重なる箇所のみに設けてもよい。さらに、その場合を含めて、圧入部１６の外周側に通し孔部１１１ａを設けない構成を採用してもよいし、あるいは、圧入部１６自体を設けない構成を採用してもよい。またさらに、締結部材１４の軸部１１４ａにおいて円筒部１１４ｃの外径を螺子部１１４ｂの螺子山の径以上に設定し、当該外径に応じて各挿通孔部１１３，１１２の内径を設定してもよい。 Specifically, the number of fastening holes 100 having the through-hole portions 111 a and the screw hole portions 111 b may be appropriately set according to the specifications of the valve timing adjusting device 1. Further, the through-hole portion 111a may be provided only in a portion where the journal portion 15 and the transmission portion 17 overlap in the axial direction, that is, only in a portion where the regions J and T in FIG. 4 overlap. Further, including that case, a configuration in which the through hole 111a is not provided on the outer peripheral side of the press-fit portion 16 may be employed, or a configuration in which the press-fit portion 16 itself is not provided may be employed. Furthermore, in the shaft portion 114a of the fastening member 14, the outer diameter of the cylindrical portion 114c is set to be equal to or larger than the screw thread diameter of the screw portion 114b, and the inner diameters of the insertion hole portions 113 and 112 are set according to the outer diameter. Also good.

駆動回転体１０については、カバー部材１３を連繋部材１２によって一体に形成してもよいし、本体部材１１と連繋部材１２との間に介装した中間部材を、それらの部材１１，１２と共に締結部材１４によって締結してもよい。また、「環状のトルク伝達部材」としては、タイミングチェーン８の代わりに、タイミングベルトを採用してもよい。さらに、「伝達部」としては、スプロケット歯１７ａを有するものの代わりに、「環状のトルク伝達部材」が掛け渡されるプーリを設けてもよい。またさらに、遊星歯車機構５としては、回転体１０，２０の双方に直接的に遊星歯車５０が歯車連繋するもの以外に、例えば回転体１０のみに歯車連繋する遊星歯車を、リンク機構等を介して間接的に回転体２０に連繋させたものを、採用してもよい。 For the drive rotator 10, the cover member 13 may be integrally formed by the connecting member 12, or an intermediate member interposed between the main body member 11 and the connecting member 12 is fastened together with the members 11 and 12. It may be fastened by the member 14. In addition, as the “annular torque transmission member”, a timing belt may be employed instead of the timing chain 8. Furthermore, as the “transmission portion”, a pulley on which an “annular torque transmission member” is stretched may be provided instead of the sprocket teeth 17a. Further, as the planetary gear mechanism 5, in addition to the planetary gear 50 that is directly gear-coupled to both of the rotating bodies 10 and 20, for example, a planetary gear that is geared only to the rotating body 10 is connected via a link mechanism or the like. Indirectly connected to the rotating body 20 may be employed.

そして、本発明は、吸気弁のバルブタイミングを調整する装置以外に、「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も、適用することができる。 In addition to a device that adjusts the valve timing of the intake valve, the present invention is a device that adjusts the valve timing of the exhaust valve as a “valve”, or a device that adjusts the valve timing of both the intake valve and the exhaust valve. Can also be applied.

１バルブタイミング調整装置、２カム軸、３アクチュエータ、４通電制御回路部、５遊星歯車機構、６ケース、７制御軸、８タイミングチェーン（トルク伝達部材）、１０駆動回転体、１１本体部材、１２連繋部材、１３カバー部材、１４締結部材、１５ジャーナル部、１６圧入部、１７伝達部、１７ａスプロケット歯、１８駆動側内歯車部、２０従動回転体、２１軸受部、２２連結部、２４従動側内歯車部、４０遊星キャリア、５０遊星歯車、５２駆動側外歯車部、５４従動側外歯車部、１００締結孔、１１１ａ通し孔部、１１１ｂ螺子孔部、１１１ｃクリアランス、１１２，１１３挿通孔部、１１４ａ軸部、１１４ｂ螺子部、１１４ｃ円筒部、１１４ｄ頭部 DESCRIPTION OF SYMBOLS 1 Valve timing adjustment apparatus, 2 Cam shaft, 3 Actuator, 4 Current supply control circuit part, 5 Planetary gear mechanism, 6 Case, 7 Control shaft, 8 Timing chain (torque transmission member), 10 Drive rotary body, 11 Main body member, 12 Connecting member, 13 Cover member, 14 Fastening member, 15 Journal part, 16 Press-fitting part, 17 Transmission part, 17a Sprocket teeth, 18 Drive side internal gear part, 20 Driven rotating body, 21 Bearing part, 22 Connecting part, 24 Driven side Internal gear part, 40 planetary carrier, 50 planetary gear, 52 drive side external gear part, 54 driven side external gear part, 100 fastening hole, 111a through hole part, 111b screw hole part, 111c clearance, 112,113 insertion hole part, 114a shaft portion, 114b screw portion, 114c cylindrical portion, 114d head

Claims

内燃機関においてクランク軸からの機関トルクの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、
前記クランク軸と連動回転する駆動回転体と、
前記カム軸と連動回転する従動回転体と、
前記駆動回転体及び前記従動回転体に連繋し、遊星運動することにより前記クランク軸及び前記カム軸間の相対位相を変化させる遊星歯車と、
を備え、前記駆動回転体は、
前記従動回転体により軸受されるジャーナル部を、内周部に形成し、環状のトルク伝達部材が掛け渡されることにより前記機関トルクが伝達される伝達部を、外周部に形成する筒状の本体部材と、
前記遊星歯車に連繋する連繋部材と、
前記連繋部材に挿通されて前記本体部材に螺合することにより、前記連繋部材を前記本体部材に締結する締結部材と、
を有するバルブタイミング調整装置において、
前記本体部材における前記ジャーナル部及び前記伝達部間に、通し孔部が設けられ、前記本体部材において前記ジャーナル部及び前記伝達部間から外れる箇所に、螺子孔部が設けられ、
前記締結部材は、前記通し孔部に前記連繋部材側から遊挿されて、前記螺子孔部に螺合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 transmission of engine torque from a crankshaft in an internal combustion engine,
A drive rotor that rotates in conjunction with the crankshaft;
A driven rotor that rotates in conjunction with the camshaft;
A planetary gear connected to the drive rotator and the driven rotator and changing a relative phase between the crankshaft and the camshaft by planetary motion;
The drive rotator comprises:
A cylindrical body that forms a journal portion that is supported by the driven rotating body on an inner peripheral portion, and that forms a transmission portion on the outer peripheral portion to which the engine torque is transmitted when an annular torque transmission member is stretched. Members,
A linking member linked to the planetary gear;
A fastening member that is inserted into the connecting member and screwed into the main body member to fasten the connecting member to the main body member;
In a valve timing adjusting device having
Between the journal part and the transmission part in the main body member, a through hole part is provided, and a screw hole part is provided in a place where the main body member is detached from between the journal part and the transmission part,
The said fastening member is loosely inserted in the said through-hole part from the said connection member side, and is screwed together in the said screw hole part, The valve timing adjustment apparatus characterized by the above-mentioned.

前記本体部材において前記通し孔部は、前記ジャーナル部及び前記伝達部が軸方向に沿って重なる箇所に、設けら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 in the main body member, the through hole portion is provided at a location where the journal portion and the transmission portion overlap in the axial direction.

前記本体部材において前記通し孔部は、前記ジャーナル部の外周側の軸方向全域及び前記伝達部の内周側の軸方向全域を包含する箇所に、設けられることを特徴とする請求項２に記載のバルブタイミング調整装置。 The said main body member WHEREIN: The said through-hole part is provided in the location which covers the axial direction whole region of the outer peripheral side of the said journal part, and the axial direction whole region of the inner peripheral side of the said transmission part. Valve timing adjustment device.

筒状の前記本体部材は、前記連繋部材が圧入される圧入部を、内周部のうち前記ジャーナル部と隣接する箇所に形成し、
前記本体部材において前記通し孔部は、前記ジャーナル部及び前記伝達部間から前記圧入部の外周側に跨って、設けられることを特徴とする請求項１〜３のいずれか一項に記載のバルブタイミング調整装置。 The cylindrical main body member is formed with a press-fit portion into which the connecting member is press-fitted at a location adjacent to the journal portion in the inner peripheral portion,
The valve according to any one of claims 1 to 3, wherein the through hole portion is provided across the outer peripheral side of the press-fitting portion from between the journal portion and the transmission portion in the main body member. Timing adjustment device.

前記伝達部は、金属製の前記本体部材に対して焼き入れ処理が施されてなることを特徴とする請求項１〜４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 4, wherein the transmission unit is subjected to a quenching process on the metal main body member.