JP5294156B2 - Variable valve operating device for internal combustion engine - Google Patents

Variable valve operating device for internal combustion engine Download PDF

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JP5294156B2
JP5294156B2 JP2009258991A JP2009258991A JP5294156B2 JP 5294156 B2 JP5294156 B2 JP 5294156B2 JP 2009258991 A JP2009258991 A JP 2009258991A JP 2009258991 A JP2009258991 A JP 2009258991A JP 5294156 B2 JP5294156 B2 JP 5294156B2
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cam
control shaft
gear
valve
shaft
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JP2011106279A (en
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宏 大澤
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Suzuki Motor Co Ltd
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Suzuki Motor Co Ltd
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Priority to JP2009258991A priority Critical patent/JP5294156B2/en
Priority to US12/941,618 priority patent/US20110107989A1/en
Priority to EP10190636A priority patent/EP2322771B1/en
Priority to CN2010105556311A priority patent/CN102061957B/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015Modifications 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
    • F01L13/0021Modifications 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 rocker arm ratio
    • F01L13/0026Modifications 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 rocker arm ratio by means of an eccentric
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015Modifications 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
    • F01L13/0063Modifications 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Description

この発明は、内燃機関の可変動弁装置に係り、特に機関弁のリフト特性を連続的に変化させる内燃機関の可変動弁装置に関する。   The present invention relates to a variable valve operating apparatus for an internal combustion engine, and more particularly to a variable valve operating apparatus for an internal combustion engine that continuously changes the lift characteristics of the engine valve.

車両の内燃機関には、内燃機関の運転状態に応じて機関弁のリフト量、作用角を連続的に変化させるために、機関弁をリフトさせる揺動カムを制御軸に揺動可能に支持し、カム軸の回転カムによって揺動するとともに揺動カムを揺動させるカムフォロアを位置変更機構を介して揺動カムに連結し、位置変更機構によってカムフォロアに対する揺動カムの相対的な位置関係を変更して機関弁のリフト特性を変更するようにした可変動弁装置を設けているものがある。   In order to continuously change the lift amount and operating angle of the engine valve in accordance with the operating state of the internal combustion engine, the internal combustion engine of the vehicle supports a swing cam for lifting the engine valve on the control shaft so as to be swingable. The cam follower that swings by the rotating cam of the cam shaft and swings the swing cam is connected to the swing cam via the position change mechanism, and the relative positional relationship of the swing cam with respect to the cam follower is changed by the position change mechanism. Some of them are provided with a variable valve gear that changes the lift characteristics of the engine valve.

特許第3799944号公報Japanese Patent No. 3799944

特許文献1に係る内燃機関の可変動弁機構および空気量制御装置は、仲介駆動機構の入力部と出力部との相対位相差を変更、つまり、カム軸と異なる制御軸(コントロールシャフト)にカムからの入力用ロッカアームとローラロッカアームヘの出力用揺動カムの位相をヘリカルスプラインの噛み合いによって変化させ、このとき、ヘリカルスプラインの噛合いの変化を制御軸の軸方向の動きによって実現している。   The variable valve mechanism and the air amount control device for an internal combustion engine according to Patent Document 1 change the relative phase difference between the input portion and the output portion of the mediation drive mechanism, that is, cam the control shaft (control shaft) different from the cam shaft. The phase of the swing cam for output to the input rocker arm and the roller rocker arm is changed by the meshing of the helical spline, and at this time, the meshing change of the helical spline is realized by the movement of the control shaft in the axial direction.

ところが、従来、上記の特許文献1に係る内燃機関の可変動弁機構においては、制御軸の軸方向の動きによって位相を制御するので、内燃機関の温度差によって気筒間でバルブリフトの誤差が大きくなるという問題点があった。これは、部品であるシリンダヘッドがアルミ製で形成され、制御軸が鉄製で形成されているので、シリンダヘッドと制御軸との長さの温度による変化が異なるからである。また、ヘリカルスプラインは、製造が難しく、コストアップの原因になるという不都合があった。
また、上記のような構成の可変動弁装置は、バルブリフト量が可変になるが、機関弁を作動するカムタイミングが固定であり、性能上不利になりやすいという不都合があった。
However, conventionally, in the variable valve mechanism of the internal combustion engine according to Patent Document 1 described above, the phase is controlled by the axial movement of the control shaft, so that the valve lift error between the cylinders is large due to the temperature difference of the internal combustion engine. There was a problem of becoming. This is because the cylinder head, which is a component, is made of aluminum and the control shaft is made of iron, so that changes in the lengths of the cylinder head and the control shaft due to temperature differ. In addition, the helical spline is difficult to manufacture and has the disadvantage of increasing costs.
In addition, the variable valve operating apparatus configured as described above has a disadvantage that the valve lift amount is variable but the cam timing for operating the engine valve is fixed, which tends to be disadvantageous in terms of performance.

そこで、この発明の目的は、部品間の熟膨張差よる機関弁毎のリフト特性のバラツキをなくすとともに、製造性を向上させる内燃機関の可変動弁装置を提供することにある。   SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a variable valve operating apparatus for an internal combustion engine that eliminates variations in lift characteristics for each engine valve due to a difference in mature expansion between parts and improves manufacturability.

この発明は、機関弁をリフトさせる揺動カムを制御軸に揺動可能に支持し、回転カムによって揺動するとともに前記揺動カムを揺動させるカムフォロアを位置変更機構を介して前記揺動カムに連結し、前記位置変更機構によって前記カムフォロアに対する前記揺動カムの相対的な位置関係を変更して前記機関弁のリフト特性を変更するようにした内燃機関の可変動弁装置において、前記制御軸に該制御軸に対して軸心が偏心する円形伏の偏心軸部を形成し、前記カムフォロアを前記偏心軸部に揺動可能に支持するとともに該カムフォロアに前記偏心軸部を回転軸とする外歯歯車を形成し、前記揺動カムに前記制御軸を回転軸とし前記外歯歯車と噛み合う内歯歯車を形成し、前記偏心軸部と前記外歯歯車と前記内歯歯車とによって前記位置変更機構を構成し、前記機関弁の開閉特性の変更時に前記制御軸を回転させ、前記偏心軸部によって前記外歯歯車を前記制御軸の軸心を中心に公転させ、前記外歯歯車の公転によって該外歯歯車に対する前記内歯歯車の噛合点を前記内歯歯車の周方向に移動させ、前記内歯歯車の噛合点の移動に伴って前記カムフォロアに対する前記揺動カムの位置を変更することを特徴とする。   According to the present invention, a swing cam for lifting an engine valve is swingably supported on a control shaft, and a cam follower that swings the swing cam and swings the swing cam via a position changing mechanism is provided on the swing cam. In the variable valve operating apparatus for an internal combustion engine, the lift shaft of the engine valve is changed by changing a relative positional relationship of the swing cam with respect to the cam follower by the position changing mechanism. A circular eccentric eccentric shaft portion having an eccentricity with respect to the control shaft is formed, and the cam follower is swingably supported by the eccentric shaft portion, and the cam follower is externally mounted with the eccentric shaft portion as a rotation shaft. Forming a toothed gear, forming an internal gear that meshes with the external gear with the control shaft as a rotation axis on the swing cam, and changing the position by the eccentric shaft portion, the external gear, and the internal gear. The control shaft is rotated at the time of changing the opening / closing characteristics of the engine valve, the external gear is revolved around the axis of the control shaft by the eccentric shaft portion, and the external gear is revolved Moving the meshing point of the internal gear with respect to the external gear in the circumferential direction of the internal gear, and changing the position of the swing cam with respect to the cam follower as the meshing point of the internal gear moves. Features.

この発明は、部品間の熟膨張差よる機関弁毎のリフト特性のバラツキをなくすとともに、製造性を向上させることができる。   The present invention can eliminate variations in lift characteristics for each engine valve due to a difference in mature expansion between components, and can improve manufacturability.

図1は内燃機関の可変動弁装置の斜視図である。(実施例)FIG. 1 is a perspective view of a variable valve operating apparatus for an internal combustion engine. (Example) 図2は内燃機関の可変動弁装置の分解図である。(実施例)FIG. 2 is an exploded view of a variable valve operating apparatus for an internal combustion engine. (Example) 図3は内燃機関の可変動弁装置の断面図である。(実施例)FIG. 3 is a cross-sectional view of a variable valve operating apparatus for an internal combustion engine. (Example) 図4(A)は機関弁の小リフト・非作動時の動作を示す図である。図4(B)は機関弁の小リフト・作動時の動作を示す図である。(実施例)FIG. 4 (A) is a view showing the operation of the engine valve during small lift / non-operation. FIG. 4B is a diagram showing an operation at the time of small lift / operation of the engine valve. (Example) 図5(A)は機関弁の大リフト・非作動時の動作を示す図である。図5(B)は機関弁の大リフト・作動時の動作を示す図である。(実施例)FIG. 5 (A) is a diagram showing the operation of the engine valve when the engine is lifted and not operated. FIG. 5B is a diagram showing the operation of the engine valve during a large lift / operation. (Example) 図6は機関弁のリフト量と開閉タイミングの関係を示す図である。(実施例)FIG. 6 is a diagram showing the relationship between the lift amount of the engine valve and the opening / closing timing. (Example)

この発明は、部品間の熟膨張差よる機関弁毎のリフト特性のバラツキをなくすとともに、製造性を向上させる目的を、制御軸の偏心軸部とカムフォロアの外歯歯車と揺動カムの内歯歯車とで位置変更機構を構成し、制御軸の回転によりカムフォロアに対する揺動カムの位置を変更して実現するものである。   The purpose of this invention is to eliminate variations in the lift characteristics of each engine valve due to the difference in mature expansion between parts, and to improve manufacturability. The position change mechanism is constituted by the gears, and the position of the swing cam with respect to the cam follower is changed by rotation of the control shaft.

図1〜図6は、この発明の実施例を示すものである。
図3において、1は車両に搭載される内燃機関である。以後、内燃機関1のクランク軸線方向を前後方向とし、シリンダ軸線方向を上下方向、クランク軸線及びシリンダ軸線と直交する方向を左右方向として説明する。
内燃機関1においては、図1〜図3に示すように、シリンダヘッドの燃焼室に連通する吸気ポートあるいは排気ポートからなるポートを開閉する吸気弁あるいは排気弁からなる機関弁2が設けられている。この機関弁2は、図3に示すように、正面視で、軸線Cが所定に傾斜し、且つ上下方向で移動可能にシリンダヘッドに支持されている。
この機関弁2は、前方に配置した一側機関弁2Aと、この一側機関弁2Aに並んで後方に配置した他側機関弁2Bとからなる。
一側機関弁2Aは、ポートの開口に接離される先端部の一側バルブヘッド3Aと、この一側バルブヘッド3Aに先端側が連設された一側バルブステム4Aとからなる。他側機関弁2Bは、ポートの開口に接離される先端部の他側バルブヘッド3Bと、この他側バルブヘッド3Bに先端側が連設された他側バルブステム4Bとからなる。
ここで、一側バルブヘッド3Aと他側バルブヘッド3Bとは、バルブヘッド3を構成する。一側バルブステム4Aと他側バルブステム4Bとは、バルブステム4を構成する。
1 to 6 show an embodiment of the present invention.
In FIG. 3, reference numeral 1 denotes an internal combustion engine mounted on a vehicle. Hereinafter, the crank axis direction of the internal combustion engine 1 will be referred to as the front-rear direction, the cylinder axis direction will be referred to as the up-down direction, and the direction orthogonal to the crank axis and the cylinder axis will be described as the left-right direction.
As shown in FIGS. 1 to 3, the internal combustion engine 1 is provided with an engine valve 2 composed of an intake valve or an exhaust valve that opens and closes a port composed of an intake port or an exhaust port communicating with the combustion chamber of the cylinder head. . As shown in FIG. 3, the engine valve 2 is supported by the cylinder head so that the axis C is inclined at a predetermined angle and is movable in the vertical direction when viewed from the front.
The engine valve 2 is composed of a one-side engine valve 2A disposed in front and an other-side engine valve 2B disposed rearward along with the one-side engine valve 2A.
The one-side engine valve 2A is composed of a one-side valve head 3A at the front end portion that is in contact with and away from the opening of the port, and a one-side valve stem 4A in which the front end side is connected to the one-side valve head 3A. The other-side engine valve 2B is composed of the other-side valve head 3B at the front end portion that is brought into contact with and separated from the opening of the port, and the other-side valve stem 4B having the front-end side connected to the other-side valve head 3B.
Here, the one-side valve head 3 </ b> A and the other-side valve head 3 </ b> B constitute the valve head 3. The one-side valve stem 4A and the other-side valve stem 4B constitute the valve stem 4.

内燃機関1には、機関弁2を軸方向(上下方向)移動して開弁・閉弁するローラフィンガーフォロア(RFF:ロッカアーム)5が設けられる。
このローラフィンガーフォロア5は、一側機関弁2Aに対応した一側ローラフィンガーフォロア5Aと、他側機関弁2Bに対応した他側ローラフィンガーフォロア5Bとからなる。
一側ローラフィンガーフォロア5Aは、水平方向で且つ左右方向に指向して配置された一側アーム部6Aと、この一側アーム部6Aの中央部位に支持した一側ローラ軸7Aに回転自在に設けられた一側ローラ8Aと、一側アーム部6Aの左端部に形成された一側バルブ当接部9Aと、一側アーム部6Aの右端部に形成された一側アジャスタ支持部10Aとを備える。この一側アジャスタ支持部10Aは、一側ハイドロリックラッシュアジャスタ11Aの頂上球部に支持される。
他側ローラフィンガーフォロア5Bは、水平方向で且つ左右方向に指向して配置された他側アーム部6Bと、この他側アーム部6Bの中央部位に支持した他側ローラ軸7Bに回転自在に設けられた他側ローラ8Bと、他側アーム部6Bの左端部に形成された他側バルブ当接部9Bと、他側アーム部6Bの右端部に形成された他側アジャスタ支持部10Bとを備える。この他側アジャスタ支持部10Bは、他側ハイドロリックラッシュアジャスタ11Bの頂上球部に支持される。
ここで、一側アーム部6Aと他側アーム部6Bとは、アーム部6を構成する。一側ローラ軸7Aと他側ローラ軸7Bとは、ローラ軸7を構成する。一側ローラ8Aと他側ローラ8Bとは、ローラ8を構成する。一側アジャスタ支持部10Aと他側アジャスタ支持部10Bとは、アジャスタ支持部10を構成する。一側ハイドロリックラッシュアジャスタ11Aと他側ハイドロリックラッシュアジャスタ11Bとは、ハイドロリックラッシュアジャスタ11を構成する。
The internal combustion engine 1 is provided with a roller finger follower (RFF: rocker arm) 5 that moves and opens and closes the engine valve 2 in the axial direction (vertical direction).
The roller finger follower 5 includes a one-side roller finger follower 5A corresponding to the one-side engine valve 2A and an other-side roller finger follower 5B corresponding to the other-side engine valve 2B.
The one-side roller finger follower 5A is rotatably provided on a one-side arm portion 6A arranged in a horizontal direction and in a left-right direction and a one-side roller shaft 7A supported on the central portion of the one-side arm portion 6A. The one side roller 8A, the one side valve contact portion 9A formed at the left end portion of the one side arm portion 6A, and the one side adjuster support portion 10A formed at the right end portion of the one side arm portion 6A. . The one-side adjuster support portion 10A is supported by the top sphere portion of the one-side hydraulic lash adjuster 11A.
The other-side roller finger follower 5B is rotatably provided on the other-side arm portion 6B arranged in the horizontal direction and in the left-right direction, and on the other-side roller shaft 7B supported on the central portion of the other-side arm portion 6B. The other side roller 8B, the other side valve contact portion 9B formed at the left end portion of the other side arm portion 6B, and the other side adjuster support portion 10B formed at the right end portion of the other side arm portion 6B. . The other side adjuster support portion 10B is supported by the top sphere portion of the other side hydraulic lash adjuster 11B.
Here, the one-side arm portion 6 </ b> A and the other-side arm portion 6 </ b> B constitute the arm portion 6. The one side roller shaft 7 </ b> A and the other side roller shaft 7 </ b> B constitute a roller shaft 7. The one side roller 8 </ b> A and the other side roller 8 </ b> B constitute a roller 8. The one-side adjuster support portion 10 </ b> A and the other-side adjuster support portion 10 </ b> B constitute the adjuster support portion 10. The one-side hydraulic lash adjuster 11 </ b> A and the other-side hydraulic lash adjuster 11 </ b> B constitute the hydraulic lash adjuster 11.

内燃機関1のシリンダヘッドには、内燃機関1のクランク軸と同期して回転し、機関弁2を動作させるカム軸12が前後方向に指向して支持されている。このカム軸12には、回転カム13が一体的に設けられている。この回転カム13は、ベース円部14と、このベース円部14から径方向に突出したカム部15とからなる。   A camshaft 12 that rotates in synchronization with the crankshaft of the internal combustion engine 1 and operates the engine valve 2 is supported on the cylinder head of the internal combustion engine 1 in the front-rear direction. A rotating cam 13 is integrally provided on the cam shaft 12. The rotating cam 13 includes a base circle portion 14 and a cam portion 15 protruding in the radial direction from the base circle portion 14.

内燃機関1には、機関弁2のリフト特性を変更する可変動弁装置16が設けられる。
この可変動弁装置16は、図1〜図3に示すように、機関弁2とカム軸12との間において、カム軸12と平行で前後方向に配置された制御軸17を備えている。この制御軸17は、電動モータ等からなるアクチュエータ18によって回転制御される。このアクチュエータ18は、制御手段19によって駆動制御される。
制御軸17は、図2、図3に示すように、前端部で所定径の一側軸部20と、後端部で一側軸部20と同一径の他側軸部21と、この一側軸部20と他側軸部21との間でこの一側軸部20及び他側軸部21の径よりも大きく且つ軸心が一側軸部20及び他側軸部21に対して所定の偏心量(オフセット)eで偏心した円形状の偏心軸部22とを一体的に形成して成り、つまり、一側軸部20及び他側軸部21の軸心O1に対して偏心軸部22の軸心O2が径方向に偏心量eで偏って設定されており、偏心軸部22は一側軸部20及び他側軸部21の軸心O1を中心に偏心回転する。
The internal combustion engine 1 is provided with a variable valve gear 16 that changes the lift characteristics of the engine valve 2.
As shown in FIGS. 1 to 3, the variable valve operating device 16 includes a control shaft 17 disposed between the engine valve 2 and the cam shaft 12 in parallel with the cam shaft 12 in the front-rear direction. The rotation of the control shaft 17 is controlled by an actuator 18 composed of an electric motor or the like. The actuator 18 is driven and controlled by the control means 19.
As shown in FIGS. 2 and 3, the control shaft 17 includes a one-side shaft portion 20 having a predetermined diameter at the front end portion, and the other-side shaft portion 21 having the same diameter as the one-side shaft portion 20 at the rear end portion. The diameter between the side shaft portion 20 and the other side shaft portion 21 is larger than the diameter of the one side shaft portion 20 and the other side shaft portion 21 and the axis is predetermined with respect to the one side shaft portion 20 and the other side shaft portion 21. And a circular eccentric shaft portion 22 that is eccentric with an eccentric amount (offset) e of the first shaft portion, that is, an eccentric shaft portion that is eccentric with respect to the axis O1 of the one side shaft portion 20 and the other side shaft portion 21. The shaft center O2 of 22 is set eccentrically in the radial direction by the amount of eccentricity e, and the eccentric shaft portion 22 rotates eccentrically about the shaft center O1 of the one side shaft portion 20 and the other side shaft portion 21.

制御軸17には、この制御軸17に揺動可能に支持されて機関弁2をリフトさせる揺動カム23が設けられる。
この揺動カム23は、一側軸部20に配設される一側揺動カム23Aと、他側軸部21に配設される他側揺動カム23Bとからなる。
一側揺動カム23Aは、一側機関弁2Aをリフトさせない一側ベース円部24Aと、この一側ベース円部24Aから径方向に突出して一側機関弁2Aをリフトさせる一側カム部25Aとを備えている。図2に示すように、一側ベース円部24Aの内周には、一側軸部20の径よりも大きな内径の一側空洞部26Aが形成されているとともに、この一側空洞部26Aの内周面に平歯車としての一側内歯歯車27Aが形成されている。一側ベース円部24Aは、その中心が一側軸部20と同軸上に配置されている。また、一側ベース円部24Aの外端部には、一側軸部20が貫通する一側軸用孔28Aを備えた一側支持部29Aが軸方向に突出して連設している。つまり、一側揺動カム23Aは、カム軸12の回転カム13のカム部15のリフトを一側ローラフィンガーフォロア5Aに伝達しない一側ベース円部24Aと、カム軸12の回転カム13のカム部15のリフトを一側ローラフィンガーフォロア5Aに伝達する一側カム部25Aとを備える。また、一側ベース円部24Aは、その中心が制御軸17の一側軸部20と同軸であるため、制御軸17が回転しても、一側ローラフィンガーフォロア5Aを押し動かすことがない。
他側揺動カム23Bは、他側機関弁2Bをリフトさせない他側ベース円部24Bと、この他側ベース円部24Bから径方向に突出して他側機関弁2Bをリフトさせる他側カム部25Bとを備えている。図2に示すように、他側ベース円部24Bの内周には、他側軸部21の径よりも大きな内径の他側空洞部26Bが形成されているとともに、この他側空洞部26Bの内周面に平歯車としての他側内歯歯車27Bが形成されている。他側ベース円部24Bは、その中心が他側軸部21と同軸上に配置されている。また、他側ベース円部24Bの外端部には、他側軸部21が貫通する他側軸用孔28Bを備えた他側支持部29Bが軸方向に突出して連設している。つまり、他側揺動カム23Bは、カム軸12の回転カム13のカム部15のリフトを他側ローラフィンガーフォロア5Bに伝達しない他側ベース円部24Bと、カム軸12の回転カム13のカム部15のリフトを他側ローラフィンガーフォロア5Bに伝達する他側カム部25Bとを備える。また、他側ベース円部24Bは、その中心が制御軸17の他側軸部21と同軸であるため、制御軸17が回転しても、他側ローラフィンガーフォロア5Bを押し動かすことがない。
ここで、一側ベース円部24Aと他側ベース円部24Bとは、揺動カム23のベース円部24を構成する。一側カム部25Aと他側カム部25Bとは、揺動カム23のカム部25を構成する。一側空洞部26Aと他側空洞部26Bとは、揺動カム23の空洞部26を構成する。一側内歯歯車27Aと他側内歯歯車27Bとは、揺動カム23の内歯歯車27を構成する。
The control shaft 17 is provided with a swing cam 23 that is supported by the control shaft 17 so as to be swingable and lifts the engine valve 2.
The swing cam 23 includes a one-side swing cam 23A disposed on the one-side shaft portion 20 and an other-side swing cam 23B disposed on the other-side shaft portion 21.
The one-side swing cam 23A includes a one-side base circle portion 24A that does not lift the one-side engine valve 2A, and a one-side cam portion 25A that protrudes in the radial direction from the one-side base circle portion 24A and lifts the one-side engine valve 2A. And. As shown in FIG. 2, a one-side cavity portion 26A having an inner diameter larger than the diameter of the one-side shaft portion 20 is formed on the inner periphery of the one-side base circle portion 24A. One side internal gear 27A as a spur gear is formed on the inner peripheral surface. The center of the one-side base circle portion 24 </ b> A is arranged coaxially with the one-side shaft portion 20. In addition, a one-side support portion 29A including a one-side shaft hole 28A through which the one-side shaft portion 20 passes is connected to the outer end portion of the one-side base circle portion 24A so as to protrude in the axial direction. That is, the one-side swing cam 23A includes the one-side base circular portion 24A that does not transmit the lift of the cam portion 15 of the rotating cam 13 of the cam shaft 12 to the one-side roller finger follower 5A, and the cam of the rotating cam 13 of the cam shaft 12. And a one-side cam portion 25A that transmits the lift of the portion 15 to the one-side roller finger follower 5A. Further, since the center of the one-side base circle portion 24A is coaxial with the one-side shaft portion 20 of the control shaft 17, even if the control shaft 17 rotates, the one-side roller finger follower 5A is not pushed and moved.
The other-side swing cam 23B includes an other-side base circle portion 24B that does not lift the other-side engine valve 2B, and an other-side cam portion 25B that protrudes radially from the other-side base circle portion 24B and lifts the other-side engine valve 2B. And. As shown in FIG. 2, an inner cavity 26B having an inner diameter larger than the diameter of the other shaft 21 is formed on the inner circumference of the other base circle 24B. The other internal gear 27B as a spur gear is formed on the inner peripheral surface. The center of the other-side base circle portion 24B is arranged coaxially with the other-side shaft portion 21. In addition, an other side support portion 29B including an other side shaft hole 28B through which the other side shaft portion 21 passes is connected to the outer end portion of the other side base circle portion 24B so as to protrude in the axial direction. That is, the other-side swing cam 23B includes the other-side base circular portion 24B that does not transmit the lift of the cam portion 15 of the rotating cam 13 of the camshaft 12 to the other-side roller finger follower 5B, and the cam of the rotating cam 13 of the camshaft 12. The other side cam part 25B which transmits the lift of the part 15 to the other side roller finger follower 5B is provided. Further, since the center of the other-side base circle portion 24B is coaxial with the other-side shaft portion 21 of the control shaft 17, the other-side roller finger follower 5B is not pushed and moved even if the control shaft 17 rotates.
Here, the one-side base circle portion 24 </ b> A and the other-side base circle portion 24 </ b> B constitute the base circle portion 24 of the swing cam 23. The one-side cam portion 25A and the other-side cam portion 25B constitute the cam portion 25 of the swing cam 23. The one side cavity portion 26 </ b> A and the other side cavity portion 26 </ b> B constitute the cavity portion 26 of the swing cam 23. The one side internal gear 27 </ b> A and the other side internal gear 27 </ b> B constitute the internal gear 27 of the swing cam 23.

揺動カム23には、位置変更機構30を介してカムフォロア(ロッカアーム)31が連結する。このカムフォロア31は、カム軸12の回転カム13によって揺動して揺動カム23を揺動させるものである。
このカムフォロア31は、制御軸17の偏心軸部22に嵌装される軸用挿通孔32を備えた管状本体33と、この管状本体33の軸方向中央部位でカム軸12側に突出した一対のローラ支持部34・34と、この一対のローラ支持部34・34に支持されたローラピン35と、一対のローラ支持部34・34間でローラピン35に回転自在に支持されたローラ36とを備え、偏心軸部22に摺動可能に支持される。
A cam follower (rocker arm) 31 is connected to the swing cam 23 via a position changing mechanism 30. The cam follower 31 swings by the rotating cam 13 of the cam shaft 12 and swings the swing cam 23.
The cam follower 31 includes a tubular body 33 having a shaft insertion hole 32 fitted to the eccentric shaft portion 22 of the control shaft 17, and a pair of protrusions projecting toward the camshaft 12 at the axial central portion of the tubular body 33. A roller support portion 34, 34, a roller pin 35 supported by the pair of roller support portions 34, 34, and a roller 36 rotatably supported by the roller pin 35 between the pair of roller support portions 34, 34; The eccentric shaft portion 22 is slidably supported.

図2、図3に示すように、管状本体33には、偏心軸部22を回転軸とし、一側揺動カム23Aの一側内歯歯車27Aに噛み合う平歯車としての一側外歯歯車37Aが前端部に形成され、偏心軸部22を回転軸とし、他側揺動カム23Bの他側内歯歯車27Bに噛みう平歯車としての他側外歯歯車37Bが後端部に形成されている。
一側外歯歯車37Aと他側外歯歯車37Bとは、カムフォロア31の外歯歯車37を構成する。
そして、一側外歯歯車37A・他側外歯歯車37B及び偏心軸部22は、一側空洞部26A・他側空洞部26Bの内側に配置される。これにより、偏心軸部22の軸方向長さを短縮させることができ、可変動弁装置16の内燃機関1への搭載性を向上できる。
図3に示すように、一側外歯歯車37A・他側外歯歯車37Bは、その軸心がカムフォロア31の揺動中心と同軸上に配置される。また、一側内歯歯車27A・他側内歯歯車27Bは、その軸心が揺動カム23の揺動中心と同軸上に配置される。よって、一側内歯歯車27A・他側内歯歯車27Bと一側外歯歯車37A・他側外歯歯車37Bとは、偏心量eだけ偏心して噛み合っている。
この実施例において、位置変更機構30は、偏心軸部22と一側内歯歯車27A・他側内歯歯車27Bと一側外歯歯車37A・他側外歯歯車37Bとによってサイクロイド機構として構成され、そして、カムフォロア31に対する一側揺動カム23A・他側揺動カム23Bの相対的な位置関係を変更して一側機関弁2A・他側機関弁2Bのリフト特性を変更する。
As shown in FIGS. 2 and 3, the tubular main body 33 has a one-side external gear 37 </ b> A as a spur gear that meshes with the one-side internal gear 27 </ b> A using the eccentric shaft portion 22 as a rotation shaft. Is formed at the front end portion, and the other side external gear 37B is formed at the rear end portion as a spur gear that meshes with the other side internal gear 27B of the other side swing cam 23B with the eccentric shaft portion 22 as the rotation shaft. Yes.
The one-side external gear 37A and the other-side external gear 37B constitute the external gear 37 of the cam follower 31.
The one-side external gear 37A, the other-side external gear 37B, and the eccentric shaft portion 22 are disposed inside the one-side cavity portion 26A and the other-side cavity portion 26B. Thereby, the axial direction length of the eccentric shaft part 22 can be shortened, and the mountability to the internal combustion engine 1 of the variable valve apparatus 16 can be improved.
As shown in FIG. 3, the axis of the one-side external gear 37 </ b> A and the other-side external gear 37 </ b> B is arranged coaxially with the swing center of the cam follower 31. The axis of the one-side internal gear 27 </ b> A and the other-side internal gear 27 </ b> B is arranged coaxially with the swing center of the swing cam 23. Therefore, the one-side internal gear 27A / other-side internal gear 27B and the one-side external gear 37A / other-side external gear 37B are eccentrically engaged by an eccentric amount e.
In this embodiment, the position changing mechanism 30 is configured as a cycloid mechanism by the eccentric shaft portion 22, the one side internal gear 27A, the other side internal gear 27B, the one side external gear 37A, and the other side external gear 37B. Then, the relative positional relationship between the one-side swing cam 23A and the other-side swing cam 23B with respect to the cam follower 31 is changed to change the lift characteristics of the one-side engine valve 2A and the other-side engine valve 2B.

図3に示すように、一側揺動カム23A・他側揺動カム23Bの一側内歯歯車27A・他側内歯歯車27Bとカムフォロア31の管状本体33の一側外歯歯車37A・他側外歯歯車37Bとは、偏心軸部22の偏心方向で噛み合うものである。よって、一側内歯歯車27A・他側内歯歯車27B及び一側外歯歯車37A・他側外歯歯車37Bの歯数は、夫々前記偏心量eで決定される。
なお、カムフォロア31の管状本体33の前端部と後端部とには一側揺動カム23Aと他側揺動カム23Bとを配置しているので、一つのカムフォロア31で二つのバルブを駆動可能とする。
As shown in FIG. 3, the one side internal gear 27A, the other side internal gear 27B, and the one side external gear 37A, etc. of the tubular body 33 of the cam follower 31 are provided. The side external gear 37B meshes with the eccentric direction of the eccentric shaft portion 22. Therefore, the number of teeth of the one-side internal gear 27A / other-side internal gear 27B and the one-side external gear 37A / other-side external gear 37B is determined by the eccentricity e.
Since the one-side swing cam 23A and the other-side swing cam 23B are arranged at the front end portion and the rear end portion of the tubular main body 33 of the cam follower 31, two valves can be driven by one cam follower 31. And

この実施例に係る可変動弁装置16の構造においては、従来のローラロッカ動弁システムに対して、カム軸12とローラフィンガーフォロア5との間に、制御軸17とカムフォロア31と揺動カム23とを追加した構造であり、図4、図5に示すように、制御軸17の回転(α)によってカムフォロア31と揺動カム23との挟み角(β)を変化させ、機関弁2のリフト量を連続的に変化させる。
なお、この可変動弁装置16は、図3に示すように、揺動カム23によってローラフィンガーフォロア5を押圧して機関弁2を動作しているが、ローラフィンガーフォロア5をタペット等と代える等して、多様な動弁系に対応可能な構造である。
In the structure of the variable valve operating apparatus 16 according to this embodiment, the control shaft 17, the cam follower 31, and the swing cam 23 are provided between the cam shaft 12 and the roller finger follower 5 with respect to the conventional roller rocker valve operating system. 4 and 5, the angle (β) between the cam follower 31 and the swing cam 23 is changed by the rotation (α) of the control shaft 17, and the lift of the engine valve 2 is Change the amount continuously.
As shown in FIG. 3, the variable valve operating device 16 operates the engine valve 2 by pressing the roller finger follower 5 by the swing cam 23. However, the roller finger follower 5 is replaced with a tappet or the like. Thus, the structure can be applied to various valve systems.

そして、可変動弁装置16においては、機関弁2の開閉特性の変更時に、制御軸17を回転させ、偏心軸部22によって外歯歯車37を制御軸17の軸心を中心に公転させ、この外歯歯車37の公転によって該外歯歯車37に対する内歯歯車27の噛合点G(図4、図5参照)を内歯歯車27の周方向に移動させ、内歯歯車27の噛合点Gの移動に伴ってカムフォロア31に対する揺動カム23の位置を変更する。
このように、制御軸17の偏心軸部22とカムフォロア31の外歯歯車37と揺動カム23の内歯歯車27とでなるサイクロイド機構により位置変更機構30を構成し、制御軸17の回転によりカムフォロア31に対する揺動カム23の位置を変更し、機関弁2のリフト特性を変更する構造としたため、機関弁2のリフト特性が制御軸17と内燃機関1との相対的な熱膨張差の影響を受けない構造にできる。
また、従来のヘリカルスプラインと比べて、製造の容易な平歯車からなる外歯歯車37と内歯歯車27とによって位置変更機構30を構成したので、構造の簡素化を図るとともに、可変動弁装置16の製造性を向上させることができる。
In the variable valve operating device 16, when changing the opening / closing characteristics of the engine valve 2, the control shaft 17 is rotated, and the external gear 37 is revolved around the axis of the control shaft 17 by the eccentric shaft portion 22. Due to the revolution of the external gear 37, the meshing point G (see FIGS. 4 and 5) of the internal gear 27 with respect to the external gear 37 is moved in the circumferential direction of the internal gear 27. Along with the movement, the position of the swing cam 23 relative to the cam follower 31 is changed.
As described above, the position changing mechanism 30 is configured by the cycloid mechanism including the eccentric shaft portion 22 of the control shaft 17, the external gear 37 of the cam follower 31, and the internal gear 27 of the swing cam 23. Since the position of the swing cam 23 relative to the cam follower 31 is changed to change the lift characteristic of the engine valve 2, the lift characteristic of the engine valve 2 is affected by the relative thermal expansion difference between the control shaft 17 and the internal combustion engine 1. It can be made a structure that does not receive
Further, since the position changing mechanism 30 is constituted by the external gear 37 and the internal gear 27 which are made of a spur gear that is easy to manufacture as compared with the conventional helical spline, the structure is simplified and the variable valve operating device is achieved. The productivity of 16 can be improved.

また、制御軸17の回転時、カムフォロア31は回転カム13との接触点が回転カム13の外周に沿って移動する一方、揺動カム23の移動により機関弁2のリフト量が変化し、機関弁2のリフト量が減少する方向に制御軸17を回転させた場合、カムフォロア31と回転カム13との接触点が回転カム13の回転方向と反対方向(進角側)へ移動する構造である。
これにより、機関弁2のリフト量を減少するにつれて機関弁2の閉じるカムタイミングを早くでき、ポンピングロスを低減できる。
Further, when the control shaft 17 rotates, the cam follower 31 moves along the outer periphery of the rotating cam 13 while the cam follower 31 moves along the outer periphery of the rotating cam 13, while the lift amount of the engine valve 2 changes due to the movement of the swing cam 23. When the control shaft 17 is rotated in a direction in which the lift amount of the valve 2 decreases, the contact point between the cam follower 31 and the rotating cam 13 moves in the direction opposite to the rotating direction of the rotating cam 13 (advance angle side). .
As a result, as the lift amount of the engine valve 2 decreases, the cam timing at which the engine valve 2 closes can be advanced, and the pumping loss can be reduced.

次いで、この可変動弁装置16のリフト時の動作を、図4、図5に基づいて説明する。
図4(A)に示すように、機関弁2の非作動時にリフト量を減少させるには、制御軸17を左回りに回転し、基準位置に対する制御軸17の回転した角度をα1とする。これに伴い、偏心軸部22によって外歯歯車37が一側軸部20及び他側軸部21の軸心O1を中心にして左回りに公転し、カムフォロア31と揺動カム23との挟み角がβ1に縮小し、且つ回転カム13とカムフォロア31との接触位置が進角方向へ移動してγ1となる。この時、回転カム13のカム部15がローラ36に接して揺動カム23を揺動させても、、図4(B)に示すように、揺動カム23とローラフィンガーフォロア5のローラ8とが殆んどベース円部24を介して接触するので、機関弁2は殆どリフトせず、リフト量は最小となる(小リフト状態)(図6のR1を参照)。
Next, the operation during lift of the variable valve device 16 will be described with reference to FIGS.
As shown in FIG. 4A, in order to decrease the lift amount when the engine valve 2 is not operated, the control shaft 17 is rotated counterclockwise, and the angle of rotation of the control shaft 17 with respect to the reference position is α1. Along with this, the external gear 37 revolves counterclockwise around the axis O1 of the one side shaft portion 20 and the other side shaft portion 21 by the eccentric shaft portion 22, and the sandwiching angle between the cam follower 31 and the swing cam 23 Is reduced to β1, and the contact position between the rotating cam 13 and the cam follower 31 moves in the advance direction to become γ1. At this time, even if the cam portion 15 of the rotating cam 13 comes into contact with the roller 36 and swings the swing cam 23, the swing cam 23 and the roller 8 of the roller finger follower 5 are moved as shown in FIG. Are almost in contact with each other via the base circle portion 24, the engine valve 2 hardly lifts, and the lift amount is minimized (small lift state) (see R1 in FIG. 6).

そして、図5(A)に示すように、機関弁2の非作動時にリフト量を増加させるには、制御軸17を左回りに回転させ、基準位置に対する角度を角度α1から角度α2に変更すると、外歯歯車37が偏心軸部22の軸心O2を中心にして右回りに自転し、そして、サイクロイド機構として働く位置変更機構30により、カムフォロア31が右方へスライド移動し(図5(A)の矢印Mで示す)、回転カム13とカムフォロア31との接触位置がγ1からγ2となり、バルブタイミングが遅角する。また、揺動カム23が一側軸部20及び他側軸部21の軸心O1を中心に右回り(開弁方向)に回転し、カムフォロア31と揺動カム23との挟み角がβ1からβ2へ拡大する。
この時、挟み角がβ2>β1であるから、図5(B)に示すように、機関弁2の作動時に、揺動カム23とローラフィンガーフォロア5とは、カム部25を介して接触する範囲が増加するので、ローラフィンガーフォロア5がハイドロリックラッシュアジャスタ11の頂上球部を中心に大きく揺動し、機関弁2が大きく作動する(大リフト状態)(図6のR2を参照)。
なお、図6に示すように、機関弁2のリフト量と開閉タイミングの関係においては、リフト量が小さくなるにつれて最大リフトの位置(リフト曲線の頂部)が進角方向へ移動する。
これは、機関弁2のリフト量を減少させると、カロフォロア31と回転カム13との接触位置が回転カム13の回転方向と逆方向(進角方向)に移動し、機関弁2の開閉タイミングが早まるからである。よって、機関弁2の小リフト時に、機関弁2を早閉じ制御可能となり、ポンピングロスの低減や燃費の向上を図ることができる。
また、従来ように制御軸の軸方向への制御を必要としないので、温度変化による部品の材料の熱膨張係数の影響を受けず、小リフトでも安定した精度を得ることが可能である。
As shown in FIG. 5A, in order to increase the lift amount when the engine valve 2 is not operated, the control shaft 17 is rotated counterclockwise and the angle with respect to the reference position is changed from the angle α1 to the angle α2. The external gear 37 rotates clockwise around the axis O2 of the eccentric shaft portion 22, and the cam follower 31 slides to the right by the position changing mechanism 30 that functions as a cycloid mechanism (FIG. 5A). The contact position between the rotating cam 13 and the cam follower 31 is changed from γ1 to γ2, and the valve timing is retarded. Further, the swing cam 23 rotates clockwise (in the valve opening direction) around the axis O1 of the one-side shaft portion 20 and the other-side shaft portion 21, and the sandwiching angle between the cam follower 31 and the swing cam 23 is from β1. Expands to β2.
At this time, since the sandwiching angle is β2> β1, the swing cam 23 and the roller finger follower 5 come into contact with each other via the cam portion 25 when the engine valve 2 is operated as shown in FIG. Since the range increases, the roller finger follower 5 swings largely around the top ball portion of the hydraulic lash adjuster 11, and the engine valve 2 operates greatly (large lift state) (see R2 in FIG. 6).
As shown in FIG. 6, in the relationship between the lift amount of the engine valve 2 and the opening / closing timing, the position of the maximum lift (the top of the lift curve) moves in the advance direction as the lift amount decreases.
This is because when the lift amount of the engine valve 2 is decreased, the contact position between the car follower 31 and the rotating cam 13 moves in the direction opposite to the rotating direction of the rotating cam 13 (advance direction), and the opening / closing timing of the engine valve 2 is Because it gets early. Therefore, when the engine valve 2 is slightly lifted, the engine valve 2 can be controlled to be quickly closed, and pumping loss can be reduced and fuel consumption can be improved.
Further, since control in the axial direction of the control shaft is not required as in the prior art, it is possible to obtain stable accuracy even with a small lift without being affected by the thermal expansion coefficient of the component material due to temperature change.

そして、この実施例において、位置変更機構30をサイクロイド機構として採用したことにより、以下のような利点を得る。
サイクロイド機構の減速原理より、αの変位角>βの変位角となる。即ち、制御軸17の回転から揺動カム23の回転をみると、(α2−α1)>(β2−β1)であり、大減速が可能となり、トルク伝達からみると、増速される側の制御軸17は、トルク変動を受けにくなる。つまり、制御軸17を駆動するアクチュエータ18の信頼性の向上につながる。
また、揺動カム23の内歯歯車27及びカムフォロア31の外歯歯車37は、外歯車と内歯車との関係であるので、大きな噛合率(歯面噛合率)を確保でき、スリップ率を小さくして歯面の信頼性向上に有利である。
更に、内歯歯車27と外歯歯車37との回転軸の偏心量eは、通常非常に小さいので、回転カム13の作動時にも、両歯車のすべりは微小であり、歯面の信頼性の向上に有利である。
And in this Example, the following advantages are acquired by employ | adopting the position change mechanism 30 as a cycloid mechanism.
Due to the deceleration principle of the cycloid mechanism, the displacement angle α is greater than the displacement angle β. That is, when the rotation of the swing cam 23 is viewed from the rotation of the control shaft 17, (α2−α1)> (β2−β1) is established, and large deceleration is possible. The control shaft 17 is less susceptible to torque fluctuations. That is, the reliability of the actuator 18 that drives the control shaft 17 is improved.
Further, since the internal gear 27 of the swing cam 23 and the external gear 37 of the cam follower 31 are in a relationship between the external gear and the internal gear, a large meshing rate (tooth surface meshing rate) can be secured, and the slip rate can be reduced. Thus, it is advantageous for improving the reliability of the tooth surface.
Further, since the eccentricity e of the rotation shafts of the internal gear 27 and the external gear 37 is usually very small, even when the rotary cam 13 is operated, the slippage of both gears is very small, and the reliability of the tooth surface can be improved. It is advantageous for improvement.

なお、この発明においては、1つのカムフォロアに2個の外歯歯車を付け、1つのカム部で2つのバルブを駆動させたが、カム部を2つ、カムフォロアを2つにする構造とすることも可能である。
また、ローラフィンガーフォロア(RFF)方式の動弁系を例にしたが、タペット等を用いて直打式の動弁系にも適用可能である。
In the present invention, two cam gears are attached to one cam follower, and two valves are driven by one cam portion. However, the cam follower has two cam followers and two cam followers. Is also possible.
Further, although a roller finger follower (RFF) type valve operating system has been described as an example, the present invention can also be applied to a direct hitting valve operating system using a tappet or the like.

この発明に係る可変動弁装置を、各種車両の内燃機関に適用可能である。   The variable valve operating apparatus according to the present invention can be applied to internal combustion engines of various vehicles.

1 内燃機関
2 機関弁
5 ローラフィンガーフォロア
12 カム軸
13 回転カム
16 可変動弁装置
17 制御軸
20 一側軸部
21 他側軸部
22 偏心軸部
23 揺動カム
23A 一側揺動カム
23B 他側揺動カム
26 空洞部
26A 一側空洞部
26B 他側空洞部
27 内歯歯車
27A 一側内歯歯車
27B 他側内歯歯車
31 カムフォロア
33 管状本体
37 外歯歯車
37A 一側外歯歯車
37B 他側外歯歯車
DESCRIPTION OF SYMBOLS 1 Internal combustion engine 2 Engine valve 5 Roller finger follower 12 Cam shaft 13 Rotating cam 16 Variable valve operating device 17 Control shaft 20 One side shaft portion 21 Other side shaft portion 22 Eccentric shaft portion 23 Swing cam 23A One side swing cam 23B Other Side swing cam 26 Cavity 26A One side cavity 26B Other side cavity 27 Internal gear 27A One side internal gear 27B Other side internal gear 31 Cam follower 33 Tubular body 37 External gear 37A One side external gear 37B Other Side external gear

Claims (3)

機関弁をリフトさせる揺動カムを制御軸に揺動可能に支持し、回転カムによって揺動するとともに前記揺動カムを揺動させるカムフォロアを位置変更機構を介して前記揺動カムに連結し、前記位置変更機構によって前記カムフォロアに対する前記揺動カムの相対的な位置関係を変更して前記機関弁のリフト特性を変更するようにした内燃機関の可変動弁装置において、前記制御軸に該制御軸に対して軸心が偏心する円形伏の偏心軸部を形成し、前記カムフォロアを前記偏心軸部に揺動可能に支持するとともに該カムフォロアに前記偏心軸部を回転軸とする外歯歯車を形成し、前記揺動カムに前記制御軸を回転軸とし前記外歯歯車と噛み合う内歯歯車を形成し、前記偏心軸部と前記外歯歯車と前記内歯歯車とによって前記位置変更機構を構成し、前記機関弁の開閉特性の変更時に前記制御軸を回転させ、前記偏心軸部によって前記外歯歯車を前記制御軸の軸心を中心に公転させ、前記外歯歯車の公転によって該外歯歯車に対する前記内歯歯車の噛合点を前記内歯歯車の周方向に移動させ、前記内歯歯車の噛合点の移動に伴って前記カムフォロアに対する前記揺動カムの位置を変更することを特徴とする内燃機関の可変動弁装置。   A swing cam that lifts the engine valve is swingably supported on the control shaft, and a cam follower that swings by the rotating cam and swings the swing cam is connected to the swing cam via a position change mechanism, In the variable valve operating apparatus for an internal combustion engine, in which the lift valve characteristic of the engine valve is changed by changing the relative positional relationship of the swing cam with respect to the cam follower by the position changing mechanism, the control shaft includes the control shaft. A circularly eccentric eccentric shaft portion having an eccentric shaft center is formed, and the cam follower is swingably supported on the eccentric shaft portion, and an external gear having the eccentric shaft portion as a rotation shaft is formed on the cam follower. An internal gear that meshes with the external gear is formed on the swing cam with the control shaft as a rotation axis, and the position change mechanism is configured by the eccentric shaft portion, the external gear, and the internal gear. When the opening / closing characteristics of the engine valve are changed, the control shaft is rotated, the eccentric shaft portion revolves the external gear around the axis of the control shaft, and the external gear revolves with respect to the external gear. An internal combustion engine characterized in that the meshing point of the internal gear is moved in the circumferential direction of the internal gear, and the position of the swing cam with respect to the cam follower is changed with the movement of the meshing point of the internal gear. Variable valve gear. 前記制御軸の回転時、前記カムフォロアは前記回転カムとの接触点が前記回転カムの外周に沿って移動する一方、前記揺動カムの移動により前記機関弁のリフト量が変化し、前記機関弁のリフト量が減少する方向に前記制御軸を回転させた場合、前記カムフォロアと前記回転カムとの接触点が前記回転カムの回転方向と反対方向へ移動する構造としたことを特徴とする請求項1に記載の内燃機関の可変動弁装置。   When the control shaft rotates, the cam follower moves along the outer periphery of the rotating cam, while the cam follower moves along the outer periphery of the rotating cam, and the lift amount of the engine valve changes due to the movement of the swing cam. The contact point between the cam follower and the rotating cam moves in a direction opposite to the rotating direction of the rotating cam when the control shaft is rotated in a direction in which the lift amount of the rotating cam decreases. 2. A variable valve operating apparatus for an internal combustion engine according to 1. 前記揺動カムは前記機関弁をリフトさせないベース円部とこのベース円部から径方向に突出するカム部とを備え、前記ベース部の内周に空洞部を形成し、この空洞部の内周面に前記内歯歯車を形成するとともに前記空洞部の内側に前記外歯歯車と前記偏心軸部とを配置したことを特徴とする請求項1に記載の内燃機関の可変動弁装置。   The swing cam includes a base circular portion that does not lift the engine valve and a cam portion that protrudes in a radial direction from the base circular portion, and a hollow portion is formed on an inner periphery of the base portion. 2. The variable valve operating apparatus for an internal combustion engine according to claim 1, wherein the internal gear is formed on a surface, and the external gear and the eccentric shaft portion are disposed inside the cavity portion.
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EP10190636A EP2322771B1 (en) 2009-11-12 2010-11-10 Variable valve operating system for internal combustion engine
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CN102061957B (en) 2013-05-08
EP2322771A1 (en) 2011-05-18

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