JP2007127090A - Variable valve mechanism - Google Patents

Variable valve mechanism Download PDF

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Publication number
JP2007127090A
JP2007127090A JP2005321850A JP2005321850A JP2007127090A JP 2007127090 A JP2007127090 A JP 2007127090A JP 2005321850 A JP2005321850 A JP 2005321850A JP 2005321850 A JP2005321850 A JP 2005321850A JP 2007127090 A JP2007127090 A JP 2007127090A
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cam
valve
passive
camshaft
valve mechanism
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JP2005321850A
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JP4469326B2 (en
Inventor
Tomiyasu Hirano
富保 平野
Ken Sugiura
憲 杉浦
Tamotsu Yamamoto
保 山本
Tetsuya Niwa
哲也 丹羽
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Otics Corp
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Otics Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0073—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "Delphi" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable valve mechanism wherein a power-transmission path from a driving cam to a valve member is simply made up of a small number of parts, and these parts are placed beside a camshaft to suppress the height of the mechanism. <P>SOLUTION: The variable valve mechanism 1 for a gasoline engine includes the camshaft 2 provided with the driving cam 5, a driven member 10 rectilinearly moved by the driving cam 5, a cam member 11 movable parallel with the movement of the driven member 10, a valve-lifter 7 opening/closing a valve 4 in response to cam-profiles 17a, 17b of the cam member 11, and an actuator 24 adjusting relative positions between the driven member 10 and the cam member 11. The driven member 10 is provided to the height nearly equal to that of the camshaft 2 with respect to a cylinder head 3, and the valve-lifter 7 is placed below the driven member 10. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、内燃機関の運転状態に応じてバルブ特性を制御する可変動弁機構に関する。   The present invention relates to a variable valve mechanism that controls valve characteristics in accordance with the operating state of an internal combustion engine.

従来、リンクを用いてバルブのリフト量、作用角および開閉タイミングを制御する可変動弁機構が知られている。例えば、図９に示す特許文献１の可変動弁機構１００は、内燃機関のクランク軸によって回転されるカムシャフト１０１を備えている。カムシャフト１０１上には、駆動カム１０２が一体回転可能に固定されるとともに、バルブリフタ１０３を駆動する揺動カム１０４が相対回動可能に支持されている。   2. Description of the Related Art Conventionally, a variable valve mechanism that uses a link to control the lift amount, working angle, and opening / closing timing of a valve is known. For example, the variable valve mechanism 100 of Patent Document 1 shown in FIG. 9 includes a camshaft 101 that is rotated by a crankshaft of an internal combustion engine. On the camshaft 101, a drive cam 102 is fixed so as to be integrally rotatable, and a swing cam 104 that drives the valve lifter 103 is supported so as to be relatively rotatable.

カムシャフト１０１と平行なコントロールシャフト１０５上には、揺動アーム１０６が可変カム１０７を介して支持されている。揺動アーム１０６の入力端はリング状リンク１０８を介して駆動カム１０２に接続され、揺動アーム１０６の出力端がロッド状リンク１０９を介して揺動カム１０４に接続されている。そして、コントロールシャフト１０５をアクチュエータで駆動し、可変カム１０７の偏心回転により揺動アーム１０６を変位させ、駆動カム１０２に対する揺動カム１０４の初期位置を調整するようになっている。
特開平１１−３２４６２５号公報 A swing arm 106 is supported via a variable cam 107 on a control shaft 105 parallel to the camshaft 101. The input end of the swing arm 106 is connected to the drive cam 102 via a ring-shaped link 108, and the output end of the swing arm 106 is connected to the swing cam 104 via a rod-shaped link 109. The control shaft 105 is driven by an actuator, and the swing arm 106 is displaced by the eccentric rotation of the variable cam 107, so that the initial position of the swing cam 104 with respect to the drive cam 102 is adjusted.
JP-A-11-324625

ところが、従来の可変動弁機構１００によると、駆動カム１０２からバルブリフタ（動弁部材）１０３までの動力伝達経路に多数の部品が必要となり、構成が複雑化する問題点があった。また、揺動アーム１０６がカムシャフト１０１の上方で上下に揺動するため、可変動弁機構１００の高さが可変機能を備えない動弁機構（駆動カム１０２がバルブリフタ１０３を直接的に駆動する機構）と比較して高くなり、可変機能の有無に応じてシリンダヘッド上部の仕様を大幅に変更する必要もあった。   However, according to the conventional variable valve mechanism 100, a large number of parts are required in the power transmission path from the drive cam 102 to the valve lifter (valve member) 103, and there is a problem that the configuration is complicated. In addition, since the swing arm 106 swings up and down above the camshaft 101, the variable valve mechanism 100 does not have a variable function in height (the drive cam 102 directly drives the valve lifter 103). It was also necessary to change the specifications of the upper part of the cylinder head according to the presence or absence of variable functions.

本発明の目的は、上記課題を解決し、駆動カムから動弁部材までの動力伝達経路を少数の部品で簡単に構成できるとともに、これらの部品をカムシャフトの横に配設して、機構高さを抑えることができる可変動弁機構を提供することにある。   The object of the present invention is to solve the above-mentioned problems and to easily configure the power transmission path from the drive cam to the valve operating member with a small number of parts, and to arrange these parts on the side of the camshaft. An object of the present invention is to provide a variable valve mechanism that can suppress this problem.

上記の課題を解決するために、本発明の可変動弁機構は、駆動カムが設けられたカムシャフトと、駆動カムによって直線移動される受動部材と、受動部材の移動方向と平行な方向へ移動可能なカム部材と、カム部材のカムプロフィールに従ってバルブを開閉する動弁部材と、受動部材とカム部材との相対位置を調整するアクチュエータとを備えたことを特徴とする。   In order to solve the above problems, the variable valve mechanism according to the present invention includes a camshaft provided with a drive cam, a passive member linearly moved by the drive cam, and a movement in a direction parallel to the moving direction of the passive member. And a valve member that opens and closes a valve according to a cam profile of the cam member, and an actuator that adjusts the relative position of the passive member and the cam member.

ここで、受動部材に関し、次の構成を採用できる。
（１）受動部材をシリンダヘッドに関してカムシャフトと略同じ高さに設け、受動部材の下側に動弁部材を配置すること。
（２）受動部材をカム部材の下側に配置すること。
（３）受動部材が駆動カムに係合するローラと、カム部材のカム面に係合するカムフォロアとを同軸に備えること。
（４）受動部材をカム部材と略同じ高さに配置すること。
（５）受動部材が駆動カムに係合する係合部と、カム部材のネジ孔に螺合するネジ軸とを備えること。 Here, the following structure is employable regarding a passive member.
(1) The passive member is provided at substantially the same height as the camshaft with respect to the cylinder head, and the valve operating member is disposed below the passive member.
(2) Disposing the passive member below the cam member.
(3) The passive member includes a roller that engages with the drive cam and a cam follower that engages with the cam surface of the cam member.
(4) The passive member is disposed at substantially the same height as the cam member.
(5) The passive member includes an engaging portion that engages with the drive cam, and a screw shaft that is screwed into the screw hole of the cam member.

カム部材に関し、次の構成を採用できる。
（６）カム部材に下向きのカム面を設け、カム面に受動部材の移動方向と平行なベース部と、ベース部より動弁部材側に迫り出すリフト部とを形成すること。
（７）カム部材を受動部材の移動方向と平行な方向へ案内する案内部材を備えること。 With respect to the cam member, the following configuration can be adopted.
(6) The cam member is provided with a downward cam surface, and a base portion parallel to the moving direction of the passive member is formed on the cam surface, and a lift portion protruding from the base portion toward the valve operating member.
(7) Provide a guide member that guides the cam member in a direction parallel to the moving direction of the passive member.

動弁部材に関し、次の構成を採用できる。
（８）動弁部材にバルブの軸線方向へ直線移動可能なバルブリフタを使用すること。
（９）動弁部材に基端を支点に揺動するロッカアームを使用すること。 Regarding the valve operating member, the following configuration can be adopted.
(8) A valve lifter that can move linearly in the axial direction of the valve is used as the valve operating member.
(9) Use a rocker arm that swings with the base end as a fulcrum for the valve member.

本発明の可変動弁機構によれば、カムシャフト上の駆動カムから動弁部材までの動力伝達経路を受動部材とカム部材の二部品で簡単に構成することができる。また、受動部材とカム部材とを平行移動可能に設けたので、両部材をカムシャフトの横に配設して、可変動弁機構の高さを低く抑えることができる。   According to the variable valve mechanism of the present invention, the power transmission path from the drive cam on the camshaft to the valve member can be easily configured with two parts, a passive member and a cam member. Further, since the passive member and the cam member are provided so as to be able to move in parallel, both members can be disposed beside the cam shaft, and the height of the variable valve mechanism can be kept low.

以下、本発明の実施形態を図面に基づいて説明する。図２、図６に示すように、この実施形態の可変動弁機構１は、駆動カム５が設けられたカムシャフト２と、駆動カム５によって直線移動される受動部材１０，３２と、受動部材１０，３２の移動方向と平行な方向へ移動可能なカム部材１１，３３と、カム部材１１，３３のカムプロフィールに従ってバルブ４を開閉する動弁部材７，３６と、受動部材１０，３２とカム部材１１，３３との相対位置を調整するアクチュエータ２４，３４とを備えている。そして、受動部材１０，３２がシリンダヘッド３に関してカムシャフト２と略同じ高さに設けられ、動弁部材７，３６が受動部材１０，３２の下側に配置されている。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIGS. 2 and 6, the variable valve mechanism 1 of this embodiment includes a camshaft 2 provided with a drive cam 5, passive members 10 and 32 that are linearly moved by the drive cam 5, and a passive member. Cam members 11, 33 movable in a direction parallel to the moving direction of 10, 32, valve members 7, 36 for opening and closing the valve 4 according to the cam profile of the cam members 11, 33, passive members 10, 32 and the cam Actuators 24 and 34 for adjusting the relative positions of the members 11 and 33 are provided. The passive members 10 and 32 are provided at substantially the same height as the camshaft 2 with respect to the cylinder head 3, and the valve members 7 and 36 are disposed below the passive members 10 and 32.

次に、本発明の実施例１を図１〜図５に基づいて説明する。この実施例の可変動弁機構１は自動車用ガソリンエンジンの吸気系に用いられている。ただし、同じ機構をガソリンエンジンの排気系に適用することも可能である。図１、図２に示すように、可変動弁機構１のカムシャフト２はシリンダヘッド３上のハウジング（図示略）に支持され、エンジンのクランク軸によって回転される。カムシャフト２上には、バルブ４と対応する位置に駆動カム５が固定され、駆動カム５にベース部５ａとノーズ部５ｂとが形成されている。   Next, Embodiment 1 of the present invention will be described with reference to FIGS. The variable valve mechanism 1 of this embodiment is used in an intake system of an automobile gasoline engine. However, the same mechanism can be applied to the exhaust system of a gasoline engine. As shown in FIGS. 1 and 2, the camshaft 2 of the variable valve mechanism 1 is supported by a housing (not shown) on the cylinder head 3 and is rotated by the crankshaft of the engine. A drive cam 5 is fixed on the camshaft 2 at a position corresponding to the valve 4, and a base portion 5 a and a nose portion 5 b are formed on the drive cam 5.

シリンダヘッド３にはバルブ４を開閉するカップ型のバルブリフタ７がバルブ４の軸線方向へ昇降可能に支持され、スプリング８によって上方へ付勢されている。バルブリフタ７の上にはブラケット９を介して受動部材１０が取り付けられ、受動部材１０の上側にカム部材１１が設けられている。受動部材１０は、駆動カム５に係合するローラ１２と、カム部材１１に係合する一対のカムフォロア１３と、ローラ１２及びカムフォロア１３を同軸に支持する中心軸１４とで構成されている。   A cup-type valve lifter 7 that opens and closes the valve 4 is supported on the cylinder head 3 so as to be movable up and down in the axial direction of the valve 4, and is urged upward by a spring 8. A passive member 10 is mounted on the valve lifter 7 via a bracket 9, and a cam member 11 is provided on the upper side of the passive member 10. The passive member 10 includes a roller 12 that engages with the drive cam 5, a pair of cam followers 13 that engage with the cam member 11, and a central shaft 14 that supports the roller 12 and the cam follower 13 coaxially.

ブラケット９には中心軸１４を支持する一対の軸受孔１５がカムシャフト２及びバルブ４の軸線に対し直角の方向（図２の左右方向）へ長く形成され、受動部材１０がバルブリフタ７上に左右方向へスライド可能に支持され、駆動カム５によって直線移動される。カム部材１１の下面にはローラ１２が嵌合する長溝１６とカムフォロア１３が係合する下向きのカム面１７とが共に左右方向へ延びるように設けられている。カム面１７には受動部材１０の移動方向と平行なベース部１７ａと、ベース部１７ａよりバルブリフタ７側へ迫り出すリフト部１７ｂとが形成され、このカムプロフィールに従ってバルブリフタ７がバルブ４を開閉するようになっている。   A pair of bearing holes 15 that support the central shaft 14 are formed in the bracket 9 so as to extend in a direction perpendicular to the axis of the camshaft 2 and the valve 4 (the left-right direction in FIG. 2). It is supported so as to be slidable in the direction and is linearly moved by the drive cam 5. On the lower surface of the cam member 11, a long groove 16 into which the roller 12 is fitted and a downward cam surface 17 with which the cam follower 13 is engaged are provided so as to extend in the left-right direction. The cam surface 17 is formed with a base portion 17a parallel to the moving direction of the passive member 10 and a lift portion 17b that protrudes from the base portion 17a to the valve lifter 7 side. The valve lifter 7 opens and closes the valve 4 according to this cam profile. It has become.

カム部材１１は受動部材１０の移動方向に長い長孔１９を備え、長孔１９を貫通するガイドシャフト２０によって受動部材１０に対し平行移動可能に支持されている。カム部材１１の上面にはラック２１が設けられ、ラック２１に噛み合うピニオン２２がコントロールシャフト２３上に挿着されている。コントロールシャフト２３は油圧又は電動のアクチュエータ２４により正逆回転され、アクチュエータ２４がエンジンの制御装置（図示略）によって制御される。そして、アクチュエータ２４が受動部材１０とカム部材１１との相対位置をエンジンの運転状態に応じて調整するようになっている。   The cam member 11 includes a long hole 19 that is long in the moving direction of the passive member 10, and is supported by a guide shaft 20 that passes through the long hole 19 so as to be movable in parallel with the passive member 10. A rack 21 is provided on the upper surface of the cam member 11, and a pinion 22 that meshes with the rack 21 is inserted on the control shaft 23. The control shaft 23 is rotated forward and backward by a hydraulic or electric actuator 24, and the actuator 24 is controlled by an engine control device (not shown). And the actuator 24 adjusts the relative position of the passive member 10 and the cam member 11 according to the driving | running state of an engine.

次に、可変動弁機構１の作用を図３〜図５に従って説明する。図３はバルブ４を最小のリフト量で開閉するときの状態を示す。このとき、アクチュエータ２４は受動部材１０とカム部材１１との相対位置を調整し、カム面１７のベース部１７ａを始端（右端）側にて受動部材１０のカムフォロア１３に接触させている（図中、Ｐはカム面１７とカムフォロア１３との初期接点位置を示す）。この状態で、カムシャフト２が回転すると、図３（ａ）に示すように、駆動カム５のベース部５ａがローラ１２に接触している期間中は、受動部材１０が移動せず、バルブリフタ７が静止し、バルブ４が閉鎖位置に保持される。   Next, the operation of the variable valve mechanism 1 will be described with reference to FIGS. FIG. 3 shows a state where the valve 4 is opened and closed with a minimum lift amount. At this time, the actuator 24 adjusts the relative position between the passive member 10 and the cam member 11, and the base portion 17a of the cam surface 17 is brought into contact with the cam follower 13 of the passive member 10 on the start end (right end) side (in the drawing). , P indicates an initial contact position between the cam surface 17 and the cam follower 13). When the camshaft 2 rotates in this state, the passive member 10 does not move during the period in which the base portion 5a of the drive cam 5 is in contact with the roller 12, as shown in FIG. Is stationary and the valve 4 is held in the closed position.

図３（ｂ）に示すように、駆動カム５のノーズ部５ｂがローラ１２に接触すると、受動部材１０が左方へ移動し、カムフォロア１３がカム面１７のリフト部１７ｂに係合する。しかし、初期接点位置Ｐがベース部１７ａの始端側に設定されているので、カムフォロア１３はリフト部１７ｂに浅く係合し、受動部材１０がバルブリフタ７を僅かに押し下げる。従って、図５の曲線（イ）に示すように、吸気バルブ４のリフト量と作用角が共に最小化される。なお、図５の曲線（ホ）は排気バルブのリフト量と作用角を示す。   As shown in FIG. 3B, when the nose portion 5 b of the drive cam 5 contacts the roller 12, the passive member 10 moves to the left, and the cam follower 13 engages with the lift portion 17 b of the cam surface 17. However, since the initial contact position P is set on the start end side of the base portion 17a, the cam follower 13 is shallowly engaged with the lift portion 17b, and the passive member 10 slightly pushes down the valve lifter 7. Accordingly, as shown by the curve (A) in FIG. 5, both the lift amount and the operating angle of the intake valve 4 are minimized. The curve (e) in FIG. 5 shows the lift amount and operating angle of the exhaust valve.

図４は吸気バルブ４を最大のリフト量で開閉するときの状態を示す。このとき、アクチュエータ２４はカム面１７とカムフォロア１３との初期接点位置Ｐをベース部１７ａの終端（左端）側に変更している。しかし、ベース部１７ａが受動部材１０の移動方向と平行に形成されているので、初期接点位置Ｐが変化しても、受動部材１０の初期高さに変化は生じない。このため、図４（ａ）に示すように、駆動カム５のベース部５ａがローラ１２に接触している期間中は、受動部材１０とバルブリフタ７が共に静止し、バルブ４が閉鎖位置に保持される。   FIG. 4 shows a state when the intake valve 4 is opened and closed with the maximum lift amount. At this time, the actuator 24 changes the initial contact position P between the cam surface 17 and the cam follower 13 to the end (left end) side of the base portion 17a. However, since the base portion 17a is formed in parallel with the moving direction of the passive member 10, even if the initial contact position P changes, the initial height of the passive member 10 does not change. Therefore, as shown in FIG. 4A, during the period in which the base portion 5a of the drive cam 5 is in contact with the roller 12, both the passive member 10 and the valve lifter 7 are stationary, and the valve 4 is held in the closed position. Is done.

図４（ｂ）に示すように、駆動カム５のノーズ部５ｂがローラ１２に接触すると、受動部材１０が左方へ移動し、カムフォロア１３がリフト部１７ｂに深く係合し、受動部材１０がバルブリフタ７を最大の下降量で押し下げる。これにより、図５の曲線（ロ）に示すように、バルブリフト量および作用角が共に最大化される。従って、アクチュエータ２４で受動部材１０とカム部材１１との相対位置を調整することにより、図５の曲線（ハ），（ニ）に示すように、バルブ特性を任意の中間値に的確に制御することができる。   As shown in FIG. 4B, when the nose portion 5b of the drive cam 5 contacts the roller 12, the passive member 10 moves to the left, the cam follower 13 is deeply engaged with the lift portion 17b, and the passive member 10 Push down the valve lifter 7 with the maximum lowering amount. Thereby, as shown by the curve (b) in FIG. 5, both the valve lift amount and the operating angle are maximized. Therefore, by adjusting the relative position between the passive member 10 and the cam member 11 by the actuator 24, the valve characteristic is accurately controlled to an arbitrary intermediate value as shown by the curves (c) and (d) in FIG. be able to.

また、この可変動弁機構１によれば、駆動カム５からバルブリフタ７までの動力伝達経路を受動部材１０とカム部材１１の二部品で簡単に構成することができる。しかも、受動部材１０とカム部材１１がカムシャフト２の横で互いに平行な関係を保って左右方向へ直線移動するので、可変動弁機構１の高さを低く抑えて、可変機能を備えない動弁機構の高さとほぼ同等にすることができる。この結果、シリンダヘッド３上部の仕様変更を最小限に抑えて、可変動弁機構１を簡単に搭載できるという利点がある。   In addition, according to the variable valve mechanism 1, the power transmission path from the drive cam 5 to the valve lifter 7 can be easily configured with two parts of the passive member 10 and the cam member 11. In addition, since the passive member 10 and the cam member 11 linearly move in the left-right direction while maintaining a parallel relationship with each other on the side of the camshaft 2, the height of the variable valve mechanism 1 is kept low, and the movement without the variable function is performed. It can be made almost equal to the height of the valve mechanism. As a result, there is an advantage that the variable valve mechanism 1 can be easily mounted while minimizing the specification change in the upper part of the cylinder head 3.

次に、本発明の実施例２を図６〜図８に基づいて説明する。実施例２の可変動弁機構３１は、図６に示すように、カムシャフト２上の駆動カム５によって左右方向へ直線移動される受動部材３２と、受動部材３２の移動方向と同じ方向へ移動可能なカム部材３３と、受動部材３２とカム部材３３との相対位置を調整するアクチュエータ３４と、アクチュエータ３４の動力を受動部材３２に伝えるコントロールシャフト３５と、カム部材３３のカムプロフィールに従ってバルブ４を開閉するロッカアーム３６とを備えている。   Next, a second embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 6, the variable valve mechanism 31 of the second embodiment moves in the same direction as the moving direction of the passive member 32 that is linearly moved in the left-right direction by the drive cam 5 on the camshaft 2. A possible cam member 33, an actuator 34 for adjusting the relative position of the passive member 32 and the cam member 33, a control shaft 35 for transmitting the power of the actuator 34 to the passive member 32, and the valve 4 according to the cam profile of the cam member 33. And a rocker arm 36 that opens and closes.

ロッカアーム３６は基端側のピボット３７により上下に揺動可能に支持され、先端にバルブ４の上端を押圧する押圧部３８が設けられ、中間部にベースローラ３９が支持されている。カム部材３３は中心部を左右方向に貫通するネジ孔４０と、ベースローラ３９に係合する下向きのカム面４１とを備え、カム面４１に受動部材３２の移動方向と平行なベース部４１ａと、ベース部４１ａよりロッカアーム３６側へ迫り出すリフト部４１ｂとが形成されている。カム部材３３の上側には、該部材３３を案内するガイドローラ４２が設けられている。   The rocker arm 36 is supported by a pivot 37 on the base end side so as to be able to swing up and down, a pressing portion 38 for pressing the upper end of the valve 4 is provided at the tip, and a base roller 39 is supported at the intermediate portion. The cam member 33 includes a screw hole 40 penetrating the center portion in the left-right direction and a downward cam surface 41 engaged with the base roller 39, and a base portion 41 a parallel to the moving direction of the passive member 32 on the cam surface 41. A lift portion 41b that protrudes toward the rocker arm 36 from the base portion 41a is formed. On the upper side of the cam member 33, a guide roller 42 for guiding the member 33 is provided.

受動部材３２は、駆動カム５に係合する係合頭部４４と、カム部材３３のネジ孔４０に螺合するネジ軸４５とを備えている。ネジ軸４５の先端にはスリット４６が形成され、スリット４６にコントロールシャフト３５の駆動キー４７がスライド可能に挿入されている。そして、アクチュエータ３４がコントロールシャフト３５を介してネジ軸４５を正逆回転し、ネジ軸４５上でカム部材３３を往復移動して、カム部材３３と受動部材３２との相対位置を調整するようになっている。なお、コントロールシャフト３５とネジ軸４５の端面間には、カム部材３３を駆動カム５側へ戻す復帰バネ４８が介装されている。   The passive member 32 includes an engaging head 44 that engages with the drive cam 5 and a screw shaft 45 that is screwed into the screw hole 40 of the cam member 33. A slit 46 is formed at the tip of the screw shaft 45, and a drive key 47 of the control shaft 35 is slidably inserted into the slit 46. Then, the actuator 34 rotates the screw shaft 45 forward and backward via the control shaft 35 and reciprocates the cam member 33 on the screw shaft 45 to adjust the relative position between the cam member 33 and the passive member 32. It has become. A return spring 48 for returning the cam member 33 to the drive cam 5 side is interposed between the end surfaces of the control shaft 35 and the screw shaft 45.

次に、可変動弁機構３１の作用を図７、図８に従って説明する。図７はバルブ４を最小のリフト量で開閉するときの状態を示す。このとき、アクチュエータ３４は受動部材３２とカム部材３３との相対位置を調整して、カム面４１のベース部４１ａを始端（右端）側にてロッカアーム３６のベースローラ３９に接触させている（図中、Ｐはカム面４１とベースローラ３９との初期接点位置を示す）。この状態で、カムシャフト２が回転すると、図７（ａ）に示すように、駆動カム５のベース部５ａが受動部材３２の係合頭部４４に接触している期間中は、受動部材３２、カム部材３３、ロッカアーム３６が共に静止し、バルブ４が閉鎖位置に保持される。   Next, the operation of the variable valve mechanism 31 will be described with reference to FIGS. FIG. 7 shows a state when the valve 4 is opened and closed with a minimum lift amount. At this time, the actuator 34 adjusts the relative position of the passive member 32 and the cam member 33 to bring the base portion 41a of the cam surface 41 into contact with the base roller 39 of the rocker arm 36 on the start end (right end) side (see FIG. P indicates the initial contact position between the cam surface 41 and the base roller 39). When the camshaft 2 rotates in this state, the passive member 32 is in a period during which the base portion 5a of the drive cam 5 is in contact with the engaging head 44 of the passive member 32 as shown in FIG. The cam member 33 and the rocker arm 36 are both stationary, and the valve 4 is held in the closed position.

図７（ｂ）に示すように、駆動カム５のノーズ部５ｂが係合頭部４４に接触すると、受動部材３２とカム部材３３が一緒に右方へ移動し、カム面４１のリフト部４１ｂがベースローラ３９に接触する。しかし、初期接点位置Ｐがベース部４１ａの始端側に設定されているので、リフト部４１ｂはベースローラ３９に浅く係合し、ロッカアーム３６が僅かに揺動する。従って、図５の曲線（イ）に示すように、吸気バルブ４のリフト量と作用角が共に最小化される。   As shown in FIG. 7B, when the nose portion 5 b of the drive cam 5 comes into contact with the engagement head 44, the passive member 32 and the cam member 33 move to the right together, and the lift portion 41 b of the cam surface 41. Comes into contact with the base roller 39. However, since the initial contact position P is set at the start end side of the base portion 41a, the lift portion 41b is shallowly engaged with the base roller 39, and the rocker arm 36 is slightly swung. Accordingly, as shown by the curve (A) in FIG. 5, both the lift amount and the operating angle of the intake valve 4 are minimized.

図８は吸気バルブ４を最大のリフト量で開閉するときの状態を示す。このとき、アクチュエータ３４はカム面４１とベースローラ３９との初期接点位置Ｐをベース部４１ａの終端（左端）側に変更している。しかし、ベース部４１ａが受動部材３２の移動方向と平行に形成されているので、初期接点位置Ｐが変化しても、ロッカアーム３６の初期位相に変化が生じない。このため、図８（ａ）に示すように、駆動カム５のベース部５ａが係合頭部４４に接触している期間中は、受動部材３２、カム部材３３、ロッカアーム３６が共に静止し、バルブ４が閉鎖位置に保持される。   FIG. 8 shows a state when the intake valve 4 is opened and closed with the maximum lift amount. At this time, the actuator 34 changes the initial contact position P between the cam surface 41 and the base roller 39 to the end (left end) side of the base portion 41a. However, since the base portion 41a is formed in parallel with the moving direction of the passive member 32, even if the initial contact position P changes, the initial phase of the rocker arm 36 does not change. For this reason, as shown in FIG. 8A, during the period in which the base portion 5a of the drive cam 5 is in contact with the engagement head 44, the passive member 32, the cam member 33, and the rocker arm 36 are all stationary. The valve 4 is held in the closed position.

図８（ｂ）に示すように、駆動カム５のノーズ部５ｂが係合頭部４４に接触すると、受動部材３２とカム部材３３とが一緒に右方へ移動し、リフト部４１ｂがベースローラ３９に深く係合し、ロッカアーム３６が最大の角度で揺動する。これにより、図５の曲線（ロ）に示すように、バルブリフト量および作用角が共に最大化される。従って、この可変動弁機構３１によっても、実施例１と同様、簡単な構成でバルブ特性を的確に制御することができる。また、カム部材３３を受動部材３２と同じ高さに設けたので、実施例１と比較し、可変動弁機構３１の高さがより低くなるという利点もある。   As shown in FIG. 8 (b), when the nose portion 5b of the drive cam 5 comes into contact with the engaging head 44, the passive member 32 and the cam member 33 move together to the right, and the lift portion 41b becomes the base roller. The rocker arm 36 swings at the maximum angle. Thereby, as shown by the curve (b) in FIG. 5, both the valve lift amount and the operating angle are maximized. Therefore, the variable valve mechanism 31 can also control the valve characteristics accurately with a simple configuration as in the first embodiment. Further, since the cam member 33 is provided at the same height as the passive member 32, there is an advantage that the height of the variable valve mechanism 31 is lower than that of the first embodiment.

本発明の実施例１を示す可変動弁機構の分解斜視図である。It is a disassembled perspective view of the variable valve mechanism which shows Example 1 of this invention. 該可変動弁機構の組付形態を示す断面図である。It is sectional drawing which shows the assembly | attachment form of this variable valve mechanism. 該可変動弁機構においてバルブリフト量を最小化するときの作用を示す機構図である。It is a mechanism figure which shows an effect | action when the valve lift amount is minimized in this variable valve mechanism. 該可変動弁機構においてバルブリフト量を最大化するときの作用を示す機構図である。It is a mechanism figure which shows an effect | action when maximizing the valve lift amount in this variable valve mechanism. バルブリフト量と作用角の関係を示す特性図である。It is a characteristic view which shows the relationship between a valve lift amount and a working angle. 本発明の実施例２を示す可変動弁機構の断面図である。It is sectional drawing of the variable valve mechanism which shows Example 2 of this invention. 該可変動弁機構においてバルブリフト量を最小化するときの作用を示す機構図である。It is a mechanism figure which shows an effect | action when the valve lift amount is minimized in this variable valve mechanism. 該可変動弁機構においてバルブリフト量を最大化するときの作用を示す機構図である。It is a mechanism figure which shows an effect | action when maximizing the valve lift amount in this variable valve mechanism. 従来の可変動弁機構を示す断面図である。It is sectional drawing which shows the conventional variable valve mechanism.

符号の説明Explanation of symbols

１ 可変動弁機構（実施例１）
２ カムシャフト
４ バルブ
５ 駆動カム
７ バルブリフタ
１０ 受動部材
１１ カム部材
１７ カム面
２３ コントロールシャフト
２４ アクチュエータ
３１ 可変動弁機構（実施例２）
３２ 受動部材
３３ カム部材
３４ アクチュエータ
３５ コントロールシャフト
３６ ロッカアーム 1 Variable valve mechanism (Example 1)
2 Camshaft 4 Valve 5 Drive Cam 7 Valve Lifter 10 Passive Member 11 Cam Member 17 Cam Surface 23 Control Shaft 24 Actuator 31 Variable Valve Mechanism (Embodiment 2)
32 Passive member 33 Cam member 34 Actuator 35 Control shaft 36 Rocker arm

Claims (1)

駆動カムが設けられたカムシャフトと、駆動カムによって直線移動される受動部材と、受動部材の移動方向と平行な方向へ移動可能なカム部材と、カム部材のカムプロフィールに従ってバルブを開閉する動弁部材と、受動部材とカム部材との相対位置を調整するアクチュエータとを備えたことを特徴とする可変動弁機構。   A camshaft provided with a drive cam, a passive member that is linearly moved by the drive cam, a cam member that is movable in a direction parallel to the moving direction of the passive member, and a valve that opens and closes the valve according to the cam profile of the cam member A variable valve mechanism comprising: a member; and an actuator for adjusting a relative position between the passive member and the cam member.
JP2005321850A 2005-11-07 2005-11-07 Variable valve mechanism Expired - Fee Related JP4469326B2 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009270561A (en) * 2008-04-30 2009-11-19 Hyundai Motor Co Ltd Continuous variable valve lift apparatus and group of continuous variable valve lift apparatus
JP2010025099A (en) * 2008-07-23 2010-02-04 Hyundai Motor Co Ltd Slidable continuously variable valve lift device
DE102013113815A1 (en) * 2013-12-11 2015-06-11 Pierburg Gmbh Transmission arrangement for a mechanically controllable valve train

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101448784B1 (en) 2013-08-27 2014-10-10 현대자동차 주식회사 Mutiple variable valve lift appratus

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009270561A (en) * 2008-04-30 2009-11-19 Hyundai Motor Co Ltd Continuous variable valve lift apparatus and group of continuous variable valve lift apparatus
KR100969377B1 (en) 2008-04-30 2010-07-09 현대자동차주식회사 Continuous variable valve lift apparatus
JP2010025099A (en) * 2008-07-23 2010-02-04 Hyundai Motor Co Ltd Slidable continuously variable valve lift device
DE102013113815A1 (en) * 2013-12-11 2015-06-11 Pierburg Gmbh Transmission arrangement for a mechanically controllable valve train
US9464540B2 (en) 2013-12-11 2016-10-11 Pierburg Gmbh Transfer assembly for a mechanically controllable valve train

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