JP2005344702A - Valve system for four-cycle internal combustion engine - Google Patents

Valve system for four-cycle internal combustion engine Download PDF

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JP2005344702A
JP2005344702A JP2004196137A JP2004196137A JP2005344702A JP 2005344702 A JP2005344702 A JP 2005344702A JP 2004196137 A JP2004196137 A JP 2004196137A JP 2004196137 A JP2004196137 A JP 2004196137A JP 2005344702 A JP2005344702 A JP 2005344702A
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shaft
rocker
roller
follower
valve
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JP4251364B2 (en
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Zenji Ishikawa
善司 石川
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Abstract

<P>PROBLEM TO BE SOLVED: To make the lift amount of an intake valve continuously variable in response to the operation of an engine. <P>SOLUTION: A connection shaft 1 is journaled to a cylinder head member 7 in parallel to a cam shaft 3 via a supporting arm 5 by a shaft 6. The connection shaft 1 is turnable around the shaft 6 journaled to the cylinder head member 7 integrally with the supporting arm 5 and a second rocker arm 19 is turnably journaled at one end to the connection shaft 1. A roller cam follower 11 and a first rocker roller follower 9 having a smaller diameter are coaxially journaled to the other end of the second rocker arm 19. The roller cam follower 11 has contact with a cam base circle 4, and the first rocker roller follower 9 has contact with a back 10-5 of the first rocker arm 10 facing the cam shaft 3. In the state of closing the valve, the connection shaft 1 is turned around the shaft 6 by a driving mechanism in which the axial center of the roller cam follower 11 is coaxial with the shaft 6 pivoting the supporting arm 5, to move the turning center of the second rocker arm 19. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は４サイクル内燃機関の動弁機構に属するものである。The present invention belongs to a valve mechanism of a four-cycle internal combustion engine.

従来の４サイクル内燃機関の動弁機構は弁のリフト時期及びリフト時間及びリフト量が固定されたものが多く、この場合機関の必要とする吸気量は絞り弁すなはちスロットルバルブにより調節されていた。In many conventional four-cycle internal combustion engines, the valve lift timing, lift time, and lift amount are fixed. In this case, the intake air amount required by the engine is adjusted by a throttle valve or throttle valve. It was.

また可変機構をもつ動弁機構であってもカム軸の位相を変える弁の開閉時期のみ可変とか、カムを複数個用いて運転状態に応じて切り替えるとかであって、特に吸気弁のリフト量を連続的に可変とするものがなかった。Even a valve mechanism with a variable mechanism can change only the opening and closing timing of the valve that changes the phase of the cam shaft, or it can switch according to the operating state using a plurality of cams. There was nothing continuously variable.

したがって、吸気量の調節は前述のようにスロットルバルブにより行われ、特に自動車等における実用運転域である低、中負荷時には吸気を絞ることによるポンピングロスが大きく発生するために、機関の効率を著しく低下させ、燃費の増大、二酸化炭素の発生量を増加させていた。Therefore, the intake air amount is adjusted by the throttle valve as described above. Especially, the pumping loss due to the throttle of the intake air is greatly generated at the time of low and medium load, which is a practical operation range in an automobile or the like. The fuel consumption was reduced and the amount of carbon dioxide generated was increased.

本発明は機関の運転状態によって、特に弁のリフト量を自在に可変とし、特に吸気弁に本発明にかかる動弁機構を用いることにより、吸気量を弁自体のみで調節することを可能とすることを目的とするものである。The present invention makes it possible to freely change the lift amount of the valve depending on the operating state of the engine, and in particular, by using the valve operating mechanism according to the present invention for the intake valve, the intake amount can be adjusted only by the valve itself. It is for the purpose.

その結果、スロットルバルブによる調節を不要にすることが出来るために、低、中負荷時のポンピングロスによる損失を低減することが出来る。As a result, since adjustment by the throttle valve can be eliminated, loss due to pumping loss at low and medium loads can be reduced.

しかし、一般的にリフト量を連続的に可変とすることは、従来の単純なＤＯＨＣ及びＳＯＨＣ機構に何らかの機構及び部材を組み込まなければならず、複雑な機構、部材を組み込めば剛性の低下、慣性質量の増加により高速時追従性、性能の低下、摩擦損失の増加を招いてしまうものである。However, in general, making the lift amount continuously variable requires that some mechanism and member be incorporated into the conventional simple DOHC and SOHC mechanism. If a complicated mechanism or member is incorporated, the rigidity is lowered and inertia is reduced. The increase in mass leads to high-speed followability, reduced performance, and increased friction loss.

そして、本発明は上記課題を解決するために、サイクルごとに直接運動する部材に、複雑な部材及び形状、多くのリンク機構を用いることなく、極めて単純で低コストな部材を用いること。In order to solve the above-mentioned problems, the present invention uses extremely simple and low-cost members that do not use complicated members and shapes and many link mechanisms as members that move directly every cycle.

それによって、慣性質量の過大な増加を防ぎ、動弁機構の高速追従性を低下させないこと。As a result, an excessive increase in the inertial mass should be prevented and the high-speed tracking performance of the valve mechanism should not be reduced.

また、単純な機構とすることにより動弁機構の剛性を維持すること。Also, maintain the rigidity of the valve mechanism by using a simple mechanism.

その結果、機関の効率の向上により、燃費の向上、二酸化炭素発生量を低減することを課題とするものである。As a result, it is an object to improve fuel efficiency and reduce carbon dioxide generation by improving engine efficiency.

カム軸３と平行に位置する支持アーム取付軸６，６−１により第一ロッカーアーム１０、１０−１の背面近隣のシリンダヘッド部材７，７−１に該支持アーム取付軸６，６−１により、支持アーム５，５−１の一端をそれぞれ軸支して回動自在とする。The support arm mounting shafts 6 and 6-1 are arranged on the cylinder head members 7 and 7-1 in the vicinity of the back surface of the first rocker arms 10 and 10-1 by the support arm mounting shafts 6 and 6-1, which are positioned in parallel with the cam shaft 3. Thus, one end of each of the support arms 5 and 5-1 is pivotally supported to be rotatable.

該支持アーム取付軸６，６−１の軸中心線Ｌは弁閉時に第一ロッカーアーム１０、１０−１の背面１０−５、１０−３に近隣する上空を通過するようにする。The shaft center line L of the support arm attachment shafts 6 and 6-1 passes through the sky adjacent to the rear surfaces 10-5 and 10-3 of the first rocker arms 10 and 10-1 when the valve is closed.

そして、支持アーム５，５−１の他端を、前記支持アーム取付軸６，６−１と平行に位置する連結軸１とそれぞれ結合し、支持アーム取付軸６，６−１を中心として支持アーム５，５−１及び連結軸１が一体として回動可能とする。The other ends of the support arms 5 and 5-1 are coupled to the connection shaft 1 positioned in parallel with the support arm attachment shafts 6 and 6-1, respectively, and are supported around the support arm attachment shafts 6 and 6-1. The arms 5 and 5-1 and the connecting shaft 1 can be rotated together.

連結軸１には第二ロッカーアーム１９の一端のボス部を軸支して、該連結軸１を中心にして回動自在とする。A boss portion at one end of the second rocker arm 19 is pivotally supported on the connecting shaft 1 so as to be rotatable about the connecting shaft 1.

そして、前記支持アーム取付軸６，６−１の軸心から連結軸１の軸心までの距離と同じ距離の第二ロッカーアーム１９の他端部に、連結軸１と平行にローラーカムフォロアー１１とそれより小径の第一ロッカーローラーフォロアー９，９−１を近隣して同心に軸支し、それぞれ回転自在とする。The roller cam follower 11 is parallel to the connecting shaft 1 at the other end of the second rocker arm 19 having the same distance as the distance from the axis of the support arm mounting shaft 6, 6-1 to the axis of the connecting shaft 1. The first rocker roller followers 9 and 9-1 having a smaller diameter are adjacently and coaxially supported so as to be freely rotatable.

弁閉時の状態に置いて、ローラーカムフォロアー１１にはカムベース円４を接触させ、第一ロッカーローラーフォロアー９，９−１には第一ロッカーアーム１０，１０−１の背面にそれぞれ接触させ、この時ローラーカムフォロアー１１及び第一ロッカーローラーフォロアー９，９−１の軸心と、前記支持アーム取付軸６，６−１とが同一軸線上にあるようにする。When the valve is closed, the cam base circle 4 is brought into contact with the roller cam follower 11, the first rocker roller followers 9 and 9-1 are brought into contact with the back surfaces of the first rocker arms 10 and 10-1, respectively. At this time, the shaft centers of the roller cam follower 11 and the first rocker roller followers 9 and 9-1 and the support arm mounting shafts 6 and 6-1 are on the same axis.

そして、上記支持アーム取付軸６，６−１を中心として、支持アーム５，５−１及び連結軸１を回動させるための駆動機構として、雄ねじ１６と雌ねじ１５を用い、雌ねじ１５を、連結軸１を結合している支持アームボス部に、連結軸１と直角に軸１４により回動自在に軸支し、該雌ねじ１５に雄ねじ１６をねじ込む。Then, male screw 16 and female screw 15 are used as a drive mechanism for rotating support arm 5, 5-1 and connecting shaft 1 around the supporting arm mounting shaft 6, 6-1, and female screw 15 is connected. A support arm boss connecting the shaft 1 is pivotally supported by a shaft 14 at a right angle to the connecting shaft 1, and a male screw 16 is screwed into the female screw 15.

該雄ねじ１６は制御モーター２３により駆動可能に軸支し、雌ねじ１５に対して雄ねじ１６を出入り可能とし、それによって前記連結軸１を回動可能とする。The male screw 16 is pivotally supported by a control motor 23 so that the male screw 16 can be moved in and out of the female screw 15, thereby allowing the connecting shaft 1 to be rotated.

制御モーター２３はエンジン部材２０に揺動可能に軸結する。The control motor 23 is pivotally connected to the engine member 20 so as to be swingable.

以上の構成のもと、機関の運転状態に応じて制御モーター２３を駆動することで、連結軸１を支持アーム取付軸６，６−１を中心に回動させることにより、該連結軸１にその一端を軸支されている第二ロッカーアーム１９の回動中心を移動させる。With the above configuration, by driving the control motor 23 according to the operating state of the engine, the connecting shaft 1 is rotated about the support arm mounting shafts 6 and 6-1, so that the connecting shaft 1 is moved. The rotation center of the second rocker arm 19 that is pivotally supported at one end is moved.

それによって、カムによって駆動されるローラーカムフォロアー１１の運動方向を変化させ、同軸に軸支されている第一ロッカーローラーフォロアー９，９−１の第一ロッカーアーム１０，１０−１を押し下げる方向の運動分力を増減させる。Thereby, the movement direction of the roller cam follower 11 driven by the cam is changed, and the first rocker arms 10 and 10-1 of the first rocker roller followers 9 and 9-1 supported coaxially are pushed down. Increase or decrease the exercise component.

それによって、弁のリフト量を連続的に可変にしようとする４サイクル内燃機関の動弁機構。Thereby, a valve operating mechanism of a four-cycle internal combustion engine which attempts to make the lift amount of the valve continuously variable.

特に予混合機関の吸気弁に本発明の動弁機構を用いれば、連続的に弁のリフト量を変えることが出来るために、機関の運転及び出力の調整に必要な吸気量を弁自体の開閉のみで調節可能となる。In particular, if the valve operating mechanism of the present invention is used for the intake valve of a premixing engine, the valve lift can be changed continuously, so that the intake amount required for engine operation and output adjustment can be adjusted by opening and closing the valve itself. It will be adjustable only.

その結果、従来用いられていたスロットルバルブを用いることなく吸気量の調節が可能となり、機関の出力制御が可能となる。As a result, the intake air amount can be adjusted without using a conventionally used throttle valve, and the engine output can be controlled.

そして、上記の目的を達するための、サイクルごとに往復運動あるいは揺動運動する動弁系の部材において、新たに付加した部材は第二ロッカーアーム１９のみである。In addition, the second rocker arm 19 is the only newly added member in the valve system that reciprocates or oscillates every cycle to achieve the above object.

したがって、動弁機構の慣性質量を、特に従来の機関の単純なＤＯＨＣ及びＳＯＨＣ形式に較べて過大にすることなく、その目的を達成するものである。Therefore, the object can be achieved without excessively increasing the inertial mass of the valve mechanism as compared with the simple DOHC and SOHC types of the conventional engine.

また、サイクルごとに運動する部材に複雑な形状、多くのリンク機構を用いることなく、極めて単純な部材第二ロッカーアーム１９をひとつ付加しただけなので低コストで、動弁機構の剛性を高くすることが出来る。In addition, since a single member second rocker arm 19 is added without using a complicated shape and many link mechanisms for the member that moves every cycle, the rigidity of the valve mechanism is increased at low cost. I can do it.

さらに、弁のリフト量の変化が連続的であるので、作動時の打音がなく高速運転時にも充分な追従性を持ち、ローラーフォロアーを用いているので摩擦損失も十分に小さいものである。Furthermore, since the change in the lift amount of the valve is continuous, there is no hitting sound during operation, and there is sufficient followability even during high-speed operation. Since a roller follower is used, the friction loss is sufficiently small.

さらに、公知技術であるカム軸の位相可変機構を本発明にかかる動弁機構に用いれば、弁の開閉時期も合わせて可変になるので弁の可変リフト、可変タイミングが可能となりその効果は倍増するものである。Furthermore, if a camshaft phase variable mechanism, which is a known technique, is used in the valve operating mechanism according to the present invention, the valve opening / closing timing can also be varied, so that the variable lift and variable timing of the valve are possible, and the effect is doubled. Is.

以上のように、高速性能を落とさずに低、中負荷時のポンピング損失による摩擦損失を低減できることから、燃費の低減、二酸化炭素発生量の低減などの地球環境の維持向上に資するものである。As described above, the friction loss due to the pumping loss at low and medium loads can be reduced without degrading the high-speed performance, which contributes to the maintenance and improvement of the global environment such as the reduction of fuel consumption and the generation amount of carbon dioxide.

以下に本発明を実施するための最良の形態を実施例について説明する。The best mode for carrying out the present invention will be described below with reference to examples.

本発明の主要な構成を示す図１について説明すれば、カム軸３と平行に位置する支持アーム取付軸６により第一ロッカーアーム１０の弁押接部の背面１０−５、これは図６に記載されている、に近隣するシリンダヘッド部材７に、該支持アーム取付軸６により支持アーム５の一端を軸支して回動自在とする。Referring to FIG. 1 showing the main configuration of the present invention, the back surface 10-5 of the valve pressing portion of the first rocker arm 10 is supported by the support arm mounting shaft 6 positioned parallel to the cam shaft 3, which is shown in FIG. One end of the support arm 5 is pivotally supported by the support arm mounting shaft 6 on a cylinder head member 7 adjacent to the cylinder head member 7 which is described.

支持アーム６−１においても上記と同様な位置関係により第一ロッカーアーム１０−１の背面１０−３近隣のシリンダヘッド部材７−１に、該支持アーム取付軸６−１により支持アーム５−１の一端を軸支して回動自在とする。Also in the support arm 6-1, the support arm 5-1 is connected to the cylinder head member 7-1 near the back surface 10-3 of the first rocker arm 10-1 by the support arm mounting shaft 6-1 by the same positional relationship as described above. One end of the shaft is pivotally supported to be freely rotatable.

該支持アーム取付軸６及び６−１の軸中心線Ｌは一致するようにし、弁閉時に第一ロッカーアーム１０及び１０−１の弁押接部に近隣し、背面部１０−５及び１０−３に近隣する上空を通過するようにする。The shaft center lines L of the support arm mounting shafts 6 and 6-1 are made to coincide with each other, close to the valve pressing portion of the first rocker arms 10 and 10-1 when the valve is closed, and the back surface portions 10-5 and 10- Pass through the sky close to 3.

そして、支持アーム５の他端部分を、前記支持アーム取付軸６と平行に位置する連結軸１とを結合する。Then, the other end portion of the support arm 5 is coupled to the connecting shaft 1 positioned in parallel with the support arm mounting shaft 6.

同様に、支持アーム５−１の他端部分を連結軸１と結合する。Similarly, the other end portion of the support arm 5-1 is coupled to the connecting shaft 1.

この場合、支持アーム５及び５−１と連結軸１との結合は回転自在に軸支してもよいが、本実施例では剛性を確保するために固定し結合する。In this case, the support arms 5 and 5-1 and the connecting shaft 1 may be rotatably supported, but in this embodiment, they are fixed and connected to ensure rigidity.

そして、支持アーム取付軸６及び６−１を中心として支持アーム５及び５−１と連結軸１が一体として回動可能とする。Then, the support arms 5 and 5-1 and the connecting shaft 1 can be rotated integrally with the support arm attachment shafts 6 and 6-1.

支持アーム５と支持アーム５−１により支持されている連結軸１において、支持アーム５と支持アーム５−１の間の連結軸１には第二ロッカーアーム１９の一端のボス部を軸支して、該連結軸１を中心に回動自在とする。In the connection shaft 1 supported by the support arm 5 and the support arm 5-1, a boss portion at one end of the second rocker arm 19 is pivotally supported on the connection shaft 1 between the support arm 5 and the support arm 5-1. Thus, it can be rotated around the connecting shaft 1.

そして、前記支持アーム取付軸６及び６−１の軸心から、連結軸１の軸心までの距離と同じ距離を持つ第二ロッカーアーム１９のフォーク状に分岐した他端部に、連結軸１と平行にローラーカムフォロアー軸８により、ローラーカムフォロアー１１を軸支して回転自在とする。Then, the other end of the second rocker arm 19 having the same distance as the distance from the axis of the support arm mounting shafts 6 and 6-1 to the axis of the connection shaft 1 is connected to the connection shaft 1. The roller cam follower 11 is pivotally supported by a roller cam follower shaft 8 in parallel with the roller cam follower shaft 8 so as to be rotatable.

該ローラーカムフォロアー１１には弁閉時の状態において、カムベース円４を接触させる。The cam base circle 4 is brought into contact with the roller cam follower 11 when the valve is closed.

該ローラーカムフォロアー１１に近隣して、第一ロッカーローラーフォロアー９を同軸心に軸支して回転自在とし、弁閉時の状態において、該第一ロッカーローラーフォロアー９を第一ロッカーアーム１０の弁押接部近隣の、カム軸側に面する背面１０−５に接触させる。In the vicinity of the roller cam follower 11, the first rocker roller follower 9 is rotatably supported by being coaxially supported. When the valve is closed, the first rocker roller follower 9 is connected to the valve of the first rocker arm 10. It is made to contact the back surface 10-5 facing the camshaft side in the vicinity of the pressing portion.

同じく、該ローラーカムフォロアー１１に近隣して、第一ロッカーローラーフォロアー９と反対側に、第一ロッカーローラーフォロアー９−１を該ローラーカムフォロアー１１と同軸心に軸支して回転自在とする。Similarly, in the vicinity of the roller cam follower 11, the first rocker roller follower 9-1 is pivotally supported coaxially with the roller cam follower 11 on the side opposite to the first rocker roller follower 9 to be rotatable.

そして、弁閉時の状態において、該第一ロッカーローラーフォロアー９−１を第一ロッカーアーム１０−１の弁押接部近隣の、カム軸側に面する背面１０−３に接触させる。And in the state at the time of valve closing, this 1st rocker roller follower 9-1 is made to contact the back surface 10-3 facing the cam shaft side near the valve pressing part of the 1st rocker arm 10-1.

そして、この弁閉時の状態において、ローラーカムフォロアー１１及び第一ロッカーローラーフォロアー９と９−１の軸心と、前記支持アーム取付軸６及び６−１との軸心とが同一軸線Ｌ上にあるようにする。In this state when the valve is closed, the axis of the roller cam follower 11 and the first rocker roller followers 9 and 9-1 and the axis of the support arm mounting shafts 6 and 6-1 are on the same axis L. To be in.

そして、支持アーム５及び５−１の連結軸１に結合しているそれぞれのボス部には止めピン１７−１と１７をそれぞれ固定して設け、押さえバネ１８のボス部の曲面に沿ってえん曲している両端を、それぞれ止めピン１７−１と１７に掛けて止める。Then, the fixing pins 17-1 and 17 are fixedly provided on the respective boss portions connected to the connecting shaft 1 of the support arms 5 and 5-1, and the boss portions of the holding spring 18 are bent along the curved surface. The bent ends are hung on the stop pins 17-1 and 17 and stopped.

該押さえバネ１８の中央部は第二ロッカーアーム１９の第一ロッカーアーム１０及び１０−１に面しているアーム部分に押し当てて、その反力によりローラーカムフォロアー１１をカムベース円４に常時押接するようにする。The central portion of the presser spring 18 is pressed against the arm portion of the second rocker arm 19 facing the first rocker arms 10 and 10-1, and the roller cam follower 11 is always pressed against the cam base circle 4 by the reaction force. Make contact.

支持アーム５−１の連結軸１を支持しているボス部にはブラケット１４−１を２枚平行に支持アーム部分の反対側のボス部に設ける。Two brackets 14-1 are provided in parallel to the boss portion on the opposite side of the support arm portion at the boss portion supporting the connecting shaft 1 of the support arm 5-1.

該ブラケット１４−１の間には雌ねじ１５を連結軸と直角の位置に軸１４により回動自在に軸支して、該雌ねじ１５には雄ねじ１６をねじ込んで挿入する。Between the brackets 14-1, a female screw 15 is pivotally supported by a shaft 14 at a position perpendicular to the connecting shaft, and a male screw 16 is screwed into the female screw 15 for insertion.

該雄ねじ１６は制御モーター２３により駆動可能に軸結し、雌ねじ１５に対して雄ねじ１６を出入り可能とし、該制御モーター２３は軸１２によりエンジン部材２０に軸支し揺動可能とする。The male screw 16 is shaft-coupled so that it can be driven by a control motor 23, and the male screw 16 can be moved in and out of the female screw 15. The control motor 23 is pivotally supported on the engine member 20 by the shaft 12 and can swing.

制御モーター２３は制御回路２１を経て、アクセルペダル２２のふみ込み量、ふみ込み速度、位置等を受信して、正転、逆転、停止位置保持等を行うもので、公知技術のサーボモーターあるいはステッピングモーター及びそれに伴う制御回路を用いる。The control motor 23 receives the swallowing amount, swallowing speed, position, etc. of the accelerator pedal 22 via the control circuit 21, and performs forward rotation, reverse rotation, stop position holding, etc. Use motor and associated control circuit.

以上のような構成のもとアクセルペダル２２の操作量に応じて、支持アーム取付軸６及び６−１を中心として、支持アーム５及び５−１を回動させ、連結している連結軸１を回動させる。In the above-described configuration, the connecting shaft 1 is connected by rotating the support arms 5 and 5-1 around the support arm mounting shafts 6 and 6-1 according to the operation amount of the accelerator pedal 22. Rotate.

当然ながら、連結軸１に連結している第二ロッカーアーム１９も、支持アーム取付軸６及び６−１の軸心と同心のローラーカムフォロアー１１の軸心を中心として回動する。Naturally, the second rocker arm 19 connected to the connecting shaft 1 also rotates around the axis of the roller cam follower 11 concentric with the axis of the support arm mounting shafts 6 and 6-1.

それによって、カムにより駆動されるローラーカムフォロアー１１の運動方向を変化させ、同軸心に軸支されている第一ロッカーローラーフォロアー９と９−１の第一ロッカーアーム１０、１０−１を押し下げる方向の運動分力を増減させる。Accordingly, the direction of movement of the roller cam follower 11 driven by the cam is changed, and the first rocker arm followers 9 and 9-1 that are pivotally supported on the coaxial axis are pushed down. Increase or decrease the movement component of.

図６に示すように、アクセルペダル２２のふみ込み量のないアイドル状態、又は少ない低負荷の状態で、連結軸１及び第二ロッカーアーム１９がＲ方向に回動し、立ち上がった位置である。As shown in FIG. 6, the connecting shaft 1 and the second rocker arm 19 rotate in the R direction and stand up in an idle state where the accelerator pedal 22 is not swallowed or in a low load state.

この位置でカムが作用すればローラーカムフォロアー１１は連結軸１を中心に回動し、その回動方向と弁１３と１３−１を押し下げる方向の運動分力との成す角度が大きいので、弁１３と１３−１を押し下げる移動量が小さく、その結果図７に示すようなリフト量Ａとなるものである。If the cam acts at this position, the roller cam follower 11 rotates about the connecting shaft 1 and the angle formed by the rotational direction and the component of motion in the direction of pushing down the valves 13 and 13-1 is large. The amount of movement that pushes down 13 and 13-1 is small, resulting in a lift amount A as shown in FIG.

図８は中負荷時の連結軸１及び第二ロッカーアーム１９の位置で、前記図６の位置よりも立ち上がりの小さいＦ方向に回動した状態である。FIG. 8 shows a state where the connecting shaft 1 and the second rocker arm 19 are rotated in the F direction, which is smaller than the position shown in FIG.

この位置でカムが作動すればローラーカムフォロアー１１は連結軸１を中心に回動し、その回動方向と弁１３と１３−１を押し下げる方向の運動分力との成す角度が前記図６の場合より小さいので、弁１３と１３−１を押し下げる移動量が図６の場合より大きくなり、その結果図９に示すようなリフト量Ｂとなるものである。When the cam is operated at this position, the roller cam follower 11 rotates about the connecting shaft 1, and the angle formed by the rotational direction and the component force of movement in the direction of pushing down the valves 13 and 13-1 is shown in FIG. Therefore, the amount of movement for depressing the valves 13 and 13-1 becomes larger than that in the case of FIG. 6, and as a result, the lift amount B is as shown in FIG.

図１０は大負荷時の連結軸１及び第二ロッカーアーム１９の位置で、前記図８の位置よりもさらに立ち上がりの小さいＦ方向に回動した状態である。FIG. 10 shows a state in which the connecting shaft 1 and the second rocker arm 19 are rotated in the F direction, which is smaller than the position shown in FIG.

この位置でカムが作動すればローラーカムフォロアー１１は連結軸１を中心に回動し、その回動方向と弁１３，１３−１を押し下げる方向の運動分力との成す角度が、前記図８の場合よりさらに少なくなり、ローラーカムフォロアー１１の回動した移動量がほとんど弁１３，１３−１を押し下げる移動量として伝達される。When the cam is operated at this position, the roller cam follower 11 rotates about the connecting shaft 1, and the angle formed by the rotation direction and the component force of movement in the direction of pushing down the valves 13 and 13-1 is shown in FIG. The amount of rotation of the roller cam follower 11 is transmitted as the amount of movement of pushing down the valves 13 and 13-1.

その結果、図１１に示すリフト量Ｃとなるものである。As a result, the lift amount C shown in FIG. 11 is obtained.

以上のように、連結軸１をＦ方向に回動させれば、その回動量に従って、ローラーカムフォロアー１１の回動した移動量の多くが弁を押し下げる移動量として伝達し、弁のリフト量を増加させる。As described above, if the connecting shaft 1 is rotated in the F direction, according to the amount of rotation, most of the amount of movement of the roller cam follower 11 is transmitted as the amount of movement that pushes down the valve, and the amount of lift of the valve is thus determined. increase.

また、該連結軸１をＲ方向に回動させれば、その回動量に従って、ローラーカムフォロアー１１の回動した移動量がより少なく弁を押し下げる移動量として伝達し、弁のリフト量を減少させる。Further, if the connecting shaft 1 is rotated in the R direction, the amount of movement of the roller cam follower 11 that is rotated is less transmitted according to the amount of rotation, and the amount of lift of the valve is reduced. .

また、Ｒ方向、Ｆ方向それぞれの方向への回動は連続的に可変可能である。Further, the rotation in the R direction and the F direction can be continuously changed.

図２に示す実施例について説明すれば、第二ロッカーアーム１９−１のフォーク状に分岐した他端部に、ローラーカムフォロアー軸８−１によりローラーカムフォロアー１１−１と第一ロッカーローラーフォロアー９−２を近隣して同軸に、それぞれ回転自在に軸支する。The embodiment shown in FIG. 2 will be described. A roller cam follower shaft 8-1 and a roller cam follower 11-1 and a first rocker roller follower 9 are connected to the other end portion of the second rocker arm 19-1 branched in a fork shape. -2 is coaxially adjacent to each other and is rotatably supported.

そして、第一ロッカーローラーフォロアー９−２はＴ字形レバーの形状をした第一ロッカーアーム１０−２の、カム軸側に面した背面１０−４に接触している。The first rocker roller follower 9-2 is in contact with the back surface 10-4 facing the cam shaft side of the first rocker arm 10-2 having a T-shaped lever shape.

該背面１０−４は第一ロッカー軸と弁押接部分との間にある第一ロッカーアーム１０−２部材のカム軸３側に面する部分である。The back surface 10-4 is a portion facing the cam shaft 3 side of the first rocker arm 10-2 member between the first rocker shaft and the valve pressing portion.

動作のしかたは前記第一の実施例と同じである。The operation is the same as in the first embodiment.

図５に示す実施例について説明すれば、第一ロッカーアームを用いることなく、直押しのバケット形のタペット３０，３０−１を用いている。The embodiment shown in FIG. 5 will be described. The directly-pressed bucket-shaped tappets 30 and 30-1 are used without using the first rocker arm.

そして、第二ロッカーアーム１９−２のフォーク状に分岐した他端部に、ローラーカムフォロアー軸８−２によりローラーカムフォロアー１１−２とタペットローラーフォロアー９−３、９−４とを近隣して同軸にそれぞれ回転自在に軸支する。And the roller cam follower 11-2 and the tappet roller followers 9-3 and 9-4 are adjacent to the other end portion of the second rocker arm 19-2 branched in the fork shape by the roller cam follower shaft 8-2. Each is pivotally supported on the same axis.

該タペットローラーフォロアー９−３、９−４はそれぞれタペット３０，３０−１の頂部３１，３１−１に弁閉時の状態において接触している。The tappet roller followers 9-3 and 9-4 are in contact with the top portions 31 and 31-1 of the tappets 30 and 30-1, respectively, when the valve is closed.

そして、カムの作動により第二ロッカーアーム１９−２が連結軸１を中心に回動したときに、該タペットローラーフォロアー９−３，９−４がタペット３０、３０−１の頂部３１，３１−１を転動しながら押し下げ可能とするものである。When the second rocker arm 19-2 is rotated about the connecting shaft 1 by the operation of the cam, the tappet roller followers 9-3, 9-4 are the top portions 31, 31- of the tappets 30, 30-1. 1 can be pushed down while rolling.

そのときの動作の原理は前記第１の実施例と同じである。The principle of operation at that time is the same as that of the first embodiment.

第一ロッカーローラフォロアーとタペットローラーフォロアーは機能と、その置かれる位置は同じであるが、説明する上で第一ロッカーアームに接触するものを第一ロッカーローラフォロアー、タペットに接触するものをタペットローラーフォロアーと名づけた。The first rocker roller follower and the tappet roller follower have the same function and position, but in the explanation, the first rocker roller follower is the one that contacts the first rocker arm, and the tappet roller is the one that contacts the tappet. I named it a follower.

本発明にかかる４サイクル内燃機関の動弁機構は、ガソリン機関を代表とする予混合機関の吸気弁を駆動する動弁機構に利用される可能性が大きい。The valve mechanism for a four-cycle internal combustion engine according to the present invention is highly likely to be used as a valve mechanism for driving an intake valve of a premixing engine represented by a gasoline engine.

本発明の主要な部分を示す立体図で第一実施例をしめす。The first embodiment is shown in a three-dimensional view showing main parts of the present invention. 本発明の主要な部分を示す立体図で第二実施例をしめす。A second embodiment is shown in a three-dimensional view showing main parts of the present invention. 図２の実施例における第二ロッカーアーム１９−１とローラーカムフォロアー１１−１と第一ロッカーローラーフォロアー９−２とローラーカムフォロアー軸８−１と第一ロッカーアーム１０−２との関係を示す図で、連結軸１と平行に切断した断面図である。The relationship between the second rocker arm 19-1, the roller cam follower 11-1, the first rocker roller follower 9-2, the roller cam follower shaft 8-1 and the first rocker arm 10-2 in the embodiment of FIG. 2 is shown. It is sectional drawing cut | disconnected in parallel with the connection axis | shaft 1 in a figure. 図１の実施例における第二ロッカーアーム１９とローラーカムフォロアー１１と第一ロッカーローラーフォロアー９，９−１とローラーカムフォロアー軸８と第一ロッカーアーム１０，１０−１との関係を示す図で、連結軸１と平行に切断した断面図である。It is a figure which shows the relationship between the 2nd rocker arm 19, the roller cam follower 11, the 1st rocker roller follower 9,9-1, the roller cam follower axis | shaft 8, and the 1st rocker arm 10,10-1 in the Example of FIG. FIG. 3 is a cross-sectional view cut in parallel with the connecting shaft 1. 第三の実施例で第一ロッカーアームをバケット形のタペット３０，３０−１としたもので、タペットローラーフォロアー９−３，９−４とタペット頂部３１，３１−１との接触している位置関係を示す連結軸１と平行に切断した断面図である。In the third embodiment, the first rocker arm is a bucket-shaped tappet 30, 30-1, and the tappet roller follower 9-3, 9-4 and the tappet top 31, 31-1 are in contact with each other. It is sectional drawing cut | disconnected in parallel with the connecting shaft 1 which shows a relationship. は図１に示す実施例でカム軸３の軸方向より見た図で、低負荷あるいはアイドル状態における連結軸１及び第二ロッカーアーム１９の位置を示す側面図。These are the figures seen from the axial direction of the camshaft 3 in the Example shown in FIG. 1, and the side view which shows the position of the connection shaft 1 and the 2nd rocker arm 19 in a low load or an idle state. は図６の位置関係において、カムが作動し連結軸１を中心に第二ロッカーアーム１９が回動し弁１３を押し下げた状態を示す側面図。FIG. 7 is a side view showing a state in which the cam is operated, the second rocker arm 19 is rotated about the connecting shaft 1 and the valve 13 is pushed down in the positional relationship of FIG. 6. は同じく図１に示す実施例で、カム軸３の軸方向より見た図で、図６に示す連結軸１及び第二ロッカーアーム１９が支持アーム取付軸６を中心にＦ方向に回動した位置で中負荷状態をしめす側面図。1 is a view as seen from the axial direction of the cam shaft 3 in the embodiment shown in FIG. 1, and the connecting shaft 1 and the second rocker arm 19 shown in FIG. 6 are rotated in the F direction around the support arm mounting shaft 6. The side view which shows a middle load state by a position. 図８の位置関係においてカムが作動し、連結軸１を中心に第二ロッカーアームー１９が回動し、弁１３を押し下げた状態を示す側面図。FIG. 9 is a side view showing a state in which the cam operates in the positional relationship of FIG. 8, the second rocker arm 19 rotates around the connecting shaft 1, and the valve 13 is pushed down. は同じく図１に示す実施例で、カム軸３軸方向より見た図で、図８に示す位置よりさらにＦ方向に連結軸１及び第二ロッカーアーム１９を回動した位置で大負荷状態を示す側面図。1 is a view as seen from the camshaft triaxial direction in the embodiment shown in FIG. 1, and in the position where the connecting shaft 1 and the second rocker arm 19 are further rotated in the F direction from the position shown in FIG. FIG. は図１０の位置関係においてカムが作動し、連結軸１を中心に第二ロッカーアーム１９が回動し、弁１３を押し下げた状態を示す側面図。FIG. 11 is a side view showing a state where the cam is operated in the positional relationship of FIG. 10, the second rocker arm 19 is rotated around the connecting shaft 1, and the valve 13 is pushed down. 連結軸１とローラーカムフォロアー１１と第二ロッカーアーム１９と第一ロッカーアーム１０の、低負荷時の幾何的な動作を示す側面図。The side view which shows the geometric operation | movement at the time of low load of the connection shaft 1, the roller cam follower 11, the 2nd rocker arm 19, and the 1st rocker arm 10. FIG. 図１２と同じ構成のもと、中負荷時の幾何的な動作を示す側面図。The side view which shows the geometric operation | movement at the time of medium load based on the same structure as FIG. 図１３と同じ構成のもと、弁閉時の中負荷時の幾何的な動作を示す側面図。The side view which shows the geometric operation | movement at the time of the medium load at the time of valve closing based on the same structure as FIG. 図１３と同じ構成のもと、高負荷時の幾何的な動作を示す側面図。The side view which shows the geometric operation | movement at the time of high load on the same structure as FIG.

符号の説明Explanation of symbols

１ 連結軸 ２ カム山 ３ カム軸
４ カムベース円 ５、 ５−１ 支持アーム
６、 ６−１ 支持アーム取付軸 ７、 ７−１ シリンダヘッド部材
８、 ８−１、 ８−２ ローラーカムフォロアー軸
９、 ９−１、 ９−２ 第一ロッカーローラーフォロアー
９−３、 ９−４、 タペットローラーフォロアー
１０、 １０−１ 第一ロッカーアーム
１０−２ Ｔ字型第一ロッカーアーム
１１、 １１−１、 １１−２ ローラーカムフォロアー
１２、 １２−１ 弁バネ
１３、１３−１ 弁
１０−３、 １０−４、 １０−５ 第一ロッカーアーム背面
１２ 軸 ２３ 制御モーター １４ 軸
１４−１ ブラケット １５ 雌ねじ １６ 雄ねじ
１７、 １７−１ 止めピン
１８ 押さえバネ
１９、 １９−１、 １９−２ 第二ロッカーアーム
２０ エンジン部材
２１ 制御回路
２２ アクセル
２５、 ２５−１ 第一ロッカー軸
３０、 ３０−１ バケット形タペット
３１、 ３１−１ タペット頂部
Ｌ，Ｌ−１ 支持アーム取付軸と同一軸心線
Ａ 低負荷時弁リフト量
Ｂ 中負荷時弁リフト量
Ｃ 高負荷時弁リフト量
Ｒ 連結軸１の低負荷側回動方向
Ｆ 連結軸１の高負荷側回動方向DESCRIPTION OF SYMBOLS 1 Connection shaft 2 Cam crest 3 Cam shaft 4 Cam base circle 5, 5-1 Support arm 6, 6-1 Support arm attachment shaft 7, 7-1 Cylinder head member 8, 8-1, 8-2 Roller cam follower shaft 9 9-1, 9-2 First rocker roller follower 9-3, 9-4, Tappet roller follower 10, 10-1 First rocker arm 10-2 T-shaped first rocker arm 11, 11-1, 11 -2 roller cam follower 12, 12-1 valve spring 13, 13-1 valve 10-3, 10-4, 10-5 first rocker arm rear surface 12 shaft 23 control motor 14 shaft 14-1 bracket 15 female screw 16 male screw 17 17-1 Stopping pin 18 Pressing spring 19, 19-1, 19-2 Second rocker arm 20 Engine member 21 Control circuit 22 Accelerator 25, 5-1 First rocker shaft 30, 30-1 Bucket type tappet 31, 31-1 Tappet top L, L-1 Same axis as support arm mounting shaft A Low valve lift amount B Medium valve lift amount C Valve lift amount at high load R Low load side rotation direction of connecting shaft 1 F High load side rotation direction of connecting shaft 1

Claims (5)

カム軸と平行に位置する支持アーム取付軸により、その軸中心線が弁閉時の第一ロッカーアームの背面に近隣する上空を通過するするように、シリンダヘッド部材に該支持アーム取付軸により、支持アームの一端を軸支して回動自在とする。
該支持アームの他端を、前記支持アーム取付軸と平行に位置する連結軸と結合し、支持アーム取付軸を中心として支持アーム及び連結軸が一体として回動可能とする。
連結軸には第二ロッカーアームの一端を軸支して、該連結軸を中心に回動自在とする。
そして、前記支持アーム取付軸の軸心から連結軸の軸心までの距離と同じ距離を持つように、第二ロッカーアームの他端部に連結軸と平行にローラーカムフォロアーとそれより小径の第一ロッカーローラーフォロアーを近隣して同心に軸支し、それぞれ回転自在とする。弁閉時の状態において、ローラーカムフォロアーにはカムベース円を接触させ、第一ロッカーローラーフォロアーには第一ロッカーアームの背面に接触させ、この時ローラーカムフォロアー及び第一ロッカーローラーフォロアーの軸心と前記支持アーム取付軸の軸心とが同一軸心線上にあるようにする。
以上の構成のもと連結軸を、支持アーム取付軸を中心に回動させることにより、該連結軸にその一端を軸支している第二ロッカーアームの回動中心を移動させる。
それによって、第一ロッカーアームの背面に接触している第一ロッカーローラーフォロアーの運動方向を変化させ、該第一ロッカーアームを押し下げる方向の運動分力を増減させ、弁のリフト量を可変にしようとする４サイクル内燃機関の動弁機構。With the support arm mounting shaft positioned in parallel with the cam shaft, the shaft center line passes through the sky adjacent to the back surface of the first rocker arm when the valve is closed. One end of the support arm is pivotally supported to be rotatable.
The other end of the support arm is coupled to a connecting shaft positioned in parallel with the support arm mounting shaft, so that the support arm and the connecting shaft can be rotated together around the support arm mounting shaft.
One end of the second rocker arm is pivotally supported on the connection shaft so that the connection shaft can rotate around the connection shaft.
A roller cam follower and a smaller diameter first roller arm follower are connected to the other end of the second rocker arm so as to have the same distance as the distance from the axis of the support arm mounting shaft to the axis of the connecting shaft. A rocker roller follower is pivoted concentrically in the vicinity so that each can rotate freely. When the valve is closed, the cam base circle is brought into contact with the roller cam follower, and the back surface of the first rocker arm is brought into contact with the first rocker roller follower. At this time, the shaft centers of the roller cam follower and the first rocker roller follower are The axis of the support arm mounting shaft is on the same axis.
With the above configuration, the connecting shaft is rotated about the support arm mounting shaft, thereby moving the rotation center of the second rocker arm having one end pivotally supported by the connecting shaft.
As a result, the movement direction of the first rocker roller follower in contact with the back surface of the first rocker arm is changed, the movement component force in the direction of pushing down the first rocker arm is increased or decreased, and the lift amount of the valve is made variable. A valve operating mechanism for a 4-cycle internal combustion engine. 請求項１におけるローラーカムフォロアーが回転しないソリッドな部材より成るカムフォロアーである請求項１記載の４サイクル内燃機関の動弁機構。2. A valve operating mechanism for a four-cycle internal combustion engine according to claim 1, wherein the roller cam follower according to claim 1 is a cam follower made of a solid member that does not rotate. 請求項１における第一ロッカーローラーフォロアーが回転しないソリッドな部材より成る第一ロッカーフォロアーである請求項１記載の４サイクル内燃機関の動弁機構。The valve operating mechanism for a four-cycle internal combustion engine according to claim 1, wherein the first rocker roller follower according to claim 1 is a first rocker follower made of a solid member that does not rotate. 請求項１における第一ロッカーアームが直押しのバケット形のタペットで、該タペットの頂部にタペットローラーフォロアーが接触している請求項１記載の４サイクル内燃機関の動弁機構。2. The valve operating mechanism for a four-cycle internal combustion engine according to claim 1, wherein the first rocker arm is a directly-pressed bucket-shaped tappet, and a tappet roller follower is in contact with the top of the tappet. 請求項４記載のタペットローラーフォロアーが、回転しないソリッドな部材より成るタペットフォロアーである請求項４記載の４サイクル内燃機関の動弁機構。5. The valve mechanism for a four-cycle internal combustion engine according to claim 4, wherein the tappet roller follower according to claim 4 is a tappet follower made of a solid member that does not rotate.
JP2004196137A 2004-06-04 2004-06-04 Valve mechanism for a 4-cycle internal combustion engine Expired - Fee Related JP4251364B2 (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006283630A (en) * 2005-03-31 2006-10-19 Honda Motor Co Ltd Valve gear of engine
JP2006283641A (en) * 2005-03-31 2006-10-19 Honda Motor Co Ltd Valve gear of engine
WO2007029458A1 (en) * 2005-09-08 2007-03-15 Honda Motor Co., Ltd. Valve drive device for engine
EP1905967A1 (en) * 2006-09-25 2008-04-02 HONDA MOTOR CO., Ltd. Variable valve lift internal combustion engine
JP2008157168A (en) * 2006-12-26 2008-07-10 Honda Motor Co Ltd Variable valve opening characteristics internal combustion engine
JP2009250230A (en) * 2008-04-01 2009-10-29 Hyundai Motor Co Ltd Variable valve actuator

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006283630A (en) * 2005-03-31 2006-10-19 Honda Motor Co Ltd Valve gear of engine
JP2006283641A (en) * 2005-03-31 2006-10-19 Honda Motor Co Ltd Valve gear of engine
JP4499597B2 (en) * 2005-03-31 2010-07-07 本田技研工業株式会社 Engine valve gear
WO2007029458A1 (en) * 2005-09-08 2007-03-15 Honda Motor Co., Ltd. Valve drive device for engine
US7779797B2 (en) 2005-09-08 2010-08-24 Honda Motor Co., Ltd. Engine valve operating system
EP1905967A1 (en) * 2006-09-25 2008-04-02 HONDA MOTOR CO., Ltd. Variable valve lift internal combustion engine
US7669564B2 (en) 2006-09-25 2010-03-02 Honda Motor Co., Ltd. Variable valve lift internal combustion engine
JP2008157168A (en) * 2006-12-26 2008-07-10 Honda Motor Co Ltd Variable valve opening characteristics internal combustion engine
JP2009250230A (en) * 2008-04-01 2009-10-29 Hyundai Motor Co Ltd Variable valve actuator

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