JPH08246824A - Reciprocating contact sliding opening/closing and continuously variable valve timing device - Google Patents
Reciprocating contact sliding opening/closing and continuously variable valve timing deviceInfo
- Publication number
- JPH08246824A JPH08246824A JP7083098A JP8309895A JPH08246824A JP H08246824 A JPH08246824 A JP H08246824A JP 7083098 A JP7083098 A JP 7083098A JP 8309895 A JP8309895 A JP 8309895A JP H08246824 A JPH08246824 A JP H08246824A
- Authority
- JP
- Japan
- Prior art keywords
- cam
- arm
- shaft
- roller
- arm shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は，弁タイミングの可変装
置に係り，複合アームの力点め連続変化と，ガイドアー
ムの往復摺動接触運動による力の伝達方法で得る特徴に
より，従来の多用なエンジンを容易にノンスロットル機
構に組替え可能にして，エンジン全回転域での最適な燃
焼の制御を容易にして，低回転域でのトルクや低燃費，
高回転域での高馬力を得る．BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable valve timing device, which has been widely used in the prior art due to the continuous change of the force point of the composite arm and the characteristic obtained by the force transmission method by the reciprocating sliding contact motion of the guide arm. The engine can be easily replaced with a non-throttle mechanism to facilitate optimum combustion control in all engine revolutions, torque and fuel consumption in the low revolution range,
Get high horsepower in high rpm range.
【０００２】[0002]
【従来の技術】従来の自動車エンジンの吸，排気弁のタ
イミング装置は，多寸法カムを使用する方法．低，高速
カムの二つのカムを切替える方法や，カムの位相を行う
装置で，基本的には円弧カムのカム山を変化させて，弁
開閉の可変を行う装置である．2. Description of the Related Art The conventional timing device for intake / exhaust valves of an automobile engine uses a multi-dimensional cam. It is a device that switches between two cams, low and high speed cam, and a device that performs the phase of the cam. Basically, it is a device that changes the cam peak of an arc cam to change the valve opening and closing.
【０００３】[0003]
【従来の技術】しかし，かかる従来の弁のタイミング装
置では，可変手段がカム自体を持って行うことで，カム
の特性により弁開閉時期や開閉時間，弁リフト量の同時
可変に限界があり，全回転域での最適な弁タイミング
と，その制御が図りにくい．2. Description of the Related Art However, in such a conventional valve timing device, since the variable means holds the cam itself, there is a limit to the simultaneous change of the valve opening / closing timing, opening / closing time, and valve lift amount due to the characteristics of the cam. Optimal valve timing in the entire rotation range and its control are difficult to achieve.
【０００４】[0004]
【発明が解決するための手段】このような点を考慮し
て，２個のメインアーム１１，１１を，セカンダリアー
ム７を有する連結軸セカンダリアームシャフト１０で一
対にして，メインアーム１１，１１の回動軸メインアー
ムシャフト１３に，止めピン１４で固定した可変カム９
で一体にした複合アームと，ガイドアームシャフト５を
軸に円弧カム２のカム山で動くローラー３と，ローラー
６を備えて一体にしたガイドアーム４とで，構成するこ
とで，メインアームシャフト１３の回動で，セカンダリ
アーム７をセカンダリアームシャフト１０を軸に動かし
て，ガイドアームシャフト５の中心から，湾曲したスリ
ッパフォロア８との接触距離を制御して，力点の連続変
化を図り，ガイドアーム４による往復接触摺動によっ
て，セカンダリアーム７を押して，戻る作用を与え，セ
カンダリアームシャフト１０と連結するメインアーム１
１，１１の弁を押すリフト量の可変と，そのコントロー
ルを行うものである（油圧でセカンダリアーム直動する
方法も可能である）．In consideration of such a point, two main arms 11 and 11 are paired with a connecting shaft secondary arm shaft 10 having a secondary arm 7 to form a pair of main arms 11 and 11. The variable cam 9 fixed to the rotary shaft main arm shaft 13 with the stop pin 14.
The main arm shaft 13 is composed of a composite arm that is integrated with the guide arm shaft 5, a roller 3 that is moved by a cam mountain of an arc cam 2 around a guide arm shaft 5, and a guide arm 4 that is integrated with a roller 6. The rotation of the secondary arm 7 moves the secondary arm shaft 10 as an axis to control the contact distance from the center of the guide arm shaft 5 to the curved slipper follower 8 to continuously change the force point. The main arm 1 that pushes the secondary arm 7 by the reciprocating contact sliding by 4 to give a returning action and connects with the secondary arm shaft 10.
The amount of lift that pushes the valves 1 and 11 is changed and its control is performed (a method of directly moving the secondary arm by hydraulic pressure is also possible).
【０００５】[0005]
【作用】かくて本発明では，図１のように，２個のメイ
ンアーム１１，１１に，セカンダリアーム７を有する連
結軸セカンダリアームシャフト１０で一対にして，可変
カム９を止めピン１４で固定して備えた，メインアーム
シャフト１３で一体にした複合アームとすることで，メ
インアームシャフト１３を矢印ＪやＫの方向に回動する
と，可変カム９が矢印ＤやＥの方向に動き，セカンダリ
アーム７がセカンダリアームシャフト１０を支点軸に，
矢印ＤやＥの方向に動く，ガイドアーム４による，セカ
ンダリアーム７の湾曲したスリッパフォロア８を押す作
動によって，メインアーム１１，１１がメインアームシ
ャフト１３を支点軸に，矢印ＦやＧの方向に動き，バル
ブ１２，１２を，矢印ＨやＩの方向に動かす．ローラー
３と，ローラー６を備えるガイドアーム４は，カムシャ
フト１と一体で矢印Ａの方向に回転（逆回転も可能）す
る円弧カム２と，ローラー３との接触を図ることで，円
弧カム２のカムプロファイルにそって，ガイドアームシ
ャフト５を支点軸に矢印ＢやＣの方向に動いて，ガイド
アーム４のローラー６で，セカンダリアーム７の湾曲し
たスリッパフォロア８を往復接触摺動する．Thus, in the present invention, as shown in FIG. 1, two main arms 11 and 11 are paired with a connecting shaft secondary arm shaft 10 having a secondary arm 7, and a variable cam 9 is fixed with a stop pin 14. By providing a composite arm that is integrally provided with the main arm shaft 13, the variable cam 9 moves in the directions of arrows D and E when the main arm shaft 13 rotates in the directions of arrows J and K, and the secondary cam 9 moves. The arm 7 uses the secondary arm shaft 10 as a fulcrum shaft,
By the operation of pushing the curved slipper follower 8 of the secondary arm 7 by the guide arm 4 that moves in the directions of arrows D and E, the main arms 11 and 11 move in the directions of arrows F and G with the main arm shaft 13 as the fulcrum axis. Movement, the valves 12, 12 are moved in the directions of arrows H and I. The guide arm 4 provided with the roller 3 and the roller 6 makes contact with the arc cam 2 that rotates together with the cam shaft 1 in the direction of the arrow A (also reverse rotation is possible), and the arc 3 The guide arm shaft 5 is moved in the directions of arrows B and C along the cam profile of the guide arm shaft 5, and the roller 6 of the guide arm 4 slides the curved slipper follower 8 of the secondary arm 7 back and forth.
【０００６】図２で示すように，セカンダリアーム７の
スリッパフォロア８の湾曲するＢ点からＣ点までの曲面
は，ガイドアームシャフト５の中心Ｌから，ローラー６
の外周Ｍの距離Ｎで，Ｌ中心で円となる曲面で構成した
もので，セカンダリアーム７が矢印Ｅの方向最大状態
で，ガイドアームシャフト５を支点軸に，ガイドアーム
４のローラー６による，スリッパフォロア８の曲面Ｂ点
からＣ点までを往復接触摺動しても，メインアーム１
１，１１がメインアームシャフト１３を支点軸に可動と
ならない位置設定による，円弧カム２，ガイドアーム
４，複合アーム，バルブ１２，１２を構成することで，
図３で示す運動図のように，カムシャフト１と矢印Ａの
方向に回転する円弧カム２と接触するローラー３がカム
山で押された時，ガイドアームシャフト５を支点軸に，
ローラー４が矢印Ｃの方向に接触摺動しても，バルブ１
２，１２の押し出し作動とならず，カム山によるガイド
アーム４Ｗ＠Ｋ押し出しが終わると，リターンスプリン
グ１５等によってガイドアーム４のローラー６が接触摺
動しながら矢印Ｂの方向に戻る作動原理で，バルブ１
２，１２の，弁開閉停止状態となる，或いは続く．As shown in FIG. 2, the curved surface of the slipper follower 8 of the secondary arm 7 from the curved point B to the point C extends from the center L of the guide arm shaft 5 to the roller 6
It is configured by a curved surface that becomes a circle at the center of L at a distance N of the outer periphery M of the secondary arm 7 in the maximum state in the direction of arrow E, with the guide arm shaft 5 serving as a fulcrum shaft and by the roller 6 of the guide arm 4. Even if the sliding surface of the slipper follower 8 from point B to point C slides back and forth, the main arm 1
By configuring the arc cam 2, the guide arm 4, the composite arm, and the valves 12, 12 by the position setting in which 1 and 11 do not move about the main arm shaft 13 as the fulcrum axis,
As shown in the motion diagram of FIG. 3, when the cam shaft 1 and the roller 3 in contact with the arcuate cam 2 rotating in the direction of arrow A are pushed by the cam crest, the guide arm shaft 5 is used as the fulcrum shaft,
Even if the roller 4 slides in the direction of arrow C, the valve 1
When the guide arms 4W @ K are not pushed out by the cam ridges and the push arms 2 and 12 are not pushed out, the return spring 15 or the like causes the roller 6 of the guide arm 4 to slide in contact and return in the direction of the arrow B. Valve 1
2,12, valve open / closed state, or continue.
【０００７】エンジンのアイドリング時は，メインアー
ムシャフト１３を矢印Ｋの方向に少し回動して，可変カ
ム９で，セカンダリアーム７を，セカンダリアームシフ
ト１０を軸に矢印Ｄの方向に動かすことで，図２で示す
ように，ガイドアームシャフト５の中心Ｌからスリッパ
フォロア８のＣ点の距離が短くなることで，ローラー３
がカム山で押されてガイドアームシャフト５を支点軸
に，ガイドアーム４が矢印Ｃの方向に動くほど，ローラ
ー６で，スリッパフォロア８を押し出す作用が働き，セ
カンダリアーム７が，可変カム９を支点にセカンダリア
ームシャフト１０を押す作働となり，セカンダリアーム
シャフト１０に連結されたメインアーム１１，１１が，
メインアームシャフト１３を支点軸に，矢印Ｇの方向に
動き，バルブ１２，１２を，矢印Ｉの方向に少し動か
す，カム山によるガイドアーム４の押し出しが終わる
と，カム山にそってリターンスプリング１５により，ガ
イドアーム４が矢印Ｂの方向に戻ることで，ガイドアー
ムシャフト５とスリッパフォロア８との接触距離が戻
り，セカンダリアー７は，バルブ１２，１２のリターン
スプリングにより，メインアーム１１，１１，セカンダ
リアームシャフト１０によって，戻される作用となって
弁閉じとなる，このことで，ピストンのポンプ効果を増
して，スワールを生成させ，低回転域でのトルクのアッ
プと，低燃費を図り，ＮＯｘの低減効果を得る．When the engine is idling, the main arm shaft 13 is slightly rotated in the direction of arrow K, and the variable cam 9 moves the secondary arm 7 in the direction of arrow D about the secondary arm shift 10. As shown in FIG. 2, as the distance from the center L of the guide arm shaft 5 to the point C of the slipper follower 8 becomes shorter, the roller 3
Is pushed by the cam mountain so that the guide arm 4 moves in the direction of the arrow C with the guide arm shaft 5 as the fulcrum shaft, the action of pushing the slipper follower 8 by the roller 6 works, and the secondary arm 7 moves the variable cam 9 The operation of pushing the secondary arm shaft 10 to the fulcrum, the main arms 11, 11 connected to the secondary arm shaft 10,
When the main arm shaft 13 is moved in the direction of arrow G about the fulcrum axis and the valves 12, 12 are moved slightly in the direction of arrow I, when the pushing of the guide arm 4 by the cam mountain ends, the return spring 15 moves along the cam mountain. As a result, the guide arm 4 returns in the direction of arrow B, the contact distance between the guide arm shaft 5 and the slipper follower 8 returns, and the secondary arm 7 is returned to the main arms 11, 11, by the return springs of the valves 12, 12. The secondary arm shaft 10 returns the valve to close the valve, which increases the pumping effect of the piston to generate swirl, which increases torque in the low rotation range and reduces fuel consumption, and NOx. To obtain the reduction effect of.
【０００８】エンジンの回転を速める（速まる）時は，
図４で示すように，メインアームシャフト１３を矢印Ｋ
の方向にさらに回動して，可変カム９で，セカンダリア
ーム７を，セカンダリアームシフト１０を軸に矢印Ｄの
方向に動かすことで，ガイドアームシャフト５の中心Ｌ
から，スリッパフォロア８のＣ点の距離がさらに短くな
ることで，ローラー３がカム山で押されて，ガイドアー
ムシャフト５を支点軸にガイドアーム４が矢印Ｃの方向
に動くほど，ローラ６で，スリッパフォロア８を押し出
す作用がさらに高まって，セカンダリアーム７が可変カ
ム９を支点に，セカンダリアームシャフト１０をさらに
押す作働となり，セカンダリアームシャフト１０に連結
されたメインアーム１１，１１が，メインアームシャフ
ト１３を支点軸に矢印Ｇの方向に大きく動き，バルブ１
２，１２を，矢印Ｉの方向に大きく動かす，カム山によ
るガイドアーム４の押し出しが終わると，カム山にそっ
てリターンスプリング１５や，バルブ１２，１２のリタ
ーンスプリングによってローラー３が戻ることで，ロー
ラー６は矢印Ｂの方向に接触摺動しながら戻り，バルブ
１２，１２のリターンスプリングにより，メインアーム
１１，１１，セカンダリアームシャフト１０が戻り，バ
ルブ１２，１２により弁閉じとなる．図５で示すよう
に，弁閉じ時期で，セカンダリアーム７を矢印ＥからＤ
まで可動しても，メインアーム１１，１１は静止状態と
なり，弁閉じの安定が図れる．このように，ガイドアー
ム４の往復接触摺動運動で弁開閉となることで，弁の加
速度による，慣性質量や，ジャンプ，バウンスの低減を
図って，弁開閉停止から最大開閉の連続可変と，そのコ
ントロールをスムーズに行う．When speeding up (accelerating) the engine,
As shown in FIG. 4, connect the main arm shaft 13 to the arrow K
Further, the secondary arm 7 is rotated by the variable cam 9 in the direction of the arrow D with the secondary arm shift 10 as the axis, so that the center L of the guide arm shaft 5 is changed.
Therefore, as the distance of the point C of the slipper follower 8 is further shortened, the roller 3 is pushed by the roller 6 as the roller 3 is pushed by the cam mountain and the guide arm 4 moves in the direction of the arrow C with the guide arm shaft 5 as the fulcrum axis. , The action of pushing out the slipper follower 8 is further enhanced, and the secondary arm 7 acts to push the secondary arm shaft 10 further with the variable cam 9 as a fulcrum, and the main arms 11 and 11 connected to the secondary arm shaft 10 become the main With the arm shaft 13 as the fulcrum axis, it moves greatly in the direction of arrow G, and the valve 1
2 and 12 are largely moved in the direction of arrow I, and when the pushing out of the guide arm 4 by the cam mountain ends, the return spring 15 and the return spring of the valves 12, 12 return the roller 3 along the cam mountain, The roller 6 returns while contacting and sliding in the direction of arrow B, the main arms 11 and 11 and the secondary arm shaft 10 return by the return springs of the valves 12 and 12, and the valves 12 and 12 close the valve. As shown in FIG. 5, the secondary arm 7 is moved from the arrow E to the arrow D at the valve closing timing.
Even if it moves up to, the main arms 11 and 11 will be in a stationary state, and the valve closing can be stabilized. In this way, the valve arm opens and closes due to the reciprocating contact sliding motion of the guide arm 4, thereby reducing inertial mass, jumps, and bounces due to the acceleration of the valve, and continuously changing from the valve open / close stop to the maximum open / close. Perform the control smoothly.
【０００９】[0009]
【実施例】図１は，本発明の，往復接触摺動開閉式・連
続可変弁タイミング装置の主要部分の分解斜面図であ
る．図２は，セカンダリアーム７の湾曲するスリッパフ
ォロア８の曲線面を構成する上での，ガイドアーム４と
の条件的係りと，円弧カム２，複合アーム，ガイドアー
ム４の構成を要約した図である．図３は，セカンダリア
ーム７の矢印Ｅの方向最大状態時の，ガイドアーム４の
往復運動による，弁開閉停止となる運動を表した図であ
る．図４は，セカンダリアーム７の矢印Ｄの方向最大状
態時の，ガイドアーム４の往復運動による，弁最大開閉
となる運動を表した図である．図５は，円弧カムのカム
ベースサークル時での，セカンダリアーム７の矢印Ｅか
らＤまでのリフト作動による，弁閉じの安定を表した図
である．各図での各主要アーム，各ローラー等の大き
さ，形や，各取り付け位置や角度，各リターンスプリン
グ等は，各エンジンや他の仕様目的によって変化し，駆
動部，ピストン，他のバルブ，シリンダー，シリンダー
ヘッド，燃焼室，一部のリターンスプリング等は説明便
宜上省略してある．DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is an exploded perspective view of a main part of a reciprocating contact sliding open / close type continuously variable valve timing device according to the present invention. FIG. 2 is a diagram summarizing the conditional relationship with the guide arm 4 in constructing the curved surface of the slipper follower 8 of the secondary arm 7, and the configuration of the arc cam 2, the composite arm, and the guide arm 4. is there. FIG. 3 is a diagram showing a motion of stopping and opening the valve due to the reciprocating motion of the guide arm 4 when the secondary arm 7 is in the maximum state in the direction of the arrow E. FIG. 4 is a diagram showing the movement of the maximum arm opening / closing by the reciprocating movement of the guide arm 4 when the secondary arm 7 is in the maximum state in the direction of arrow D. FIG. 5 is a diagram showing the stability of valve closing by the lift operation from the arrow E to the arrow D of the secondary arm 7 during the cam base circle of the arc cam. The size and shape of each main arm, each roller, etc., each mounting position and angle, each return spring, etc. in each figure change depending on each engine and other specification purpose, and drive parts, pistons, other valves, The cylinder, cylinder head, combustion chamber, some return springs, etc. are omitted for convenience of explanation.
【００１０】図１で示すように，セカンダリアーム７を
有するセカンダリアームシャフト１０で，メインアーム
１１，１１を連結して一対にし，可変カム９を止めピン
１４で備えたメインアームシャフト１３で一体にした複
合アームにして，メインアームシャフト１３がシリンダ
ーヘッドに取り付くことで，メインアーム１１，１１が
矢印ＦやＧの方向に動き，メインアームシャフト１３を
エンジンの各回転域の条件に応じた，或いはノンスロッ
トルエンジンとして，スロットルバルブ無しの吸入空気
量の制御を行ってエンジンの各回転域制御を得る目的
で，油圧やギャー等で，矢印ＪやＫの方向に回動し，可
変カム９でセカンダリアーム７を矢印ＤやＥの方向に動
かし（直接シリンダー等で油圧で動かすことも可能），
ガイドアーム４のローラー３を，カムシャフト１と回転
する円弧カム２のカムプロファイルと接触させ，シリン
ダーヘッドに取り付くガイドアームシャフト５を支点軸
に，リターンスプリング１５の作用を得てガイドアーム
４を矢印ＢやＣの方向に往復運動を行わせ，ローラー６
とセカンダリアーム７の湾曲したスリッパフォロア８
が，図２で示すような構成条件，ガイドアームシャフト
５の中心Ｌから，ローラー６の外周Ｍの距離Ｎで，Ｌ中
心で円となる曲面にして，セカンダリアーム７が矢印Ｅ
の方向最大状態で，ガイドアームシャフト５を支点軸に
ガイドアーム４のローラー６で，スリッパフォロア８を
Ｂ点からＣ点まで往復接触摺動した時，メインアーム１
１，１１がメインアームシャフト１３を軸に可動しない
位置で設定による，円弧カム２，ガイドアーム４，複合
アーム，バルブ１２の構成を持って，シリンダーヘッド
内に組入れる．As shown in FIG. 1, with a secondary arm shaft 10 having a secondary arm 7, main arms 11, 11 are connected to form a pair, and a variable cam 9 is integrally provided with a main arm shaft 13 provided with a locking pin 14. When the main arm shaft 13 is attached to the cylinder head, the main arms 11 and 11 move in the directions of arrows F and G, and the main arm shaft 13 is moved in accordance with the conditions of each engine rotation range. As a non-throttle engine, for the purpose of controlling the intake air amount without a throttle valve and controlling each rotation range of the engine, the hydraulic cam or gear is used to rotate in the directions of arrows J and K, and the variable cam 9 is used as a secondary engine. Move the arm 7 in the direction of arrow D or E (it can also be hydraulically moved directly with a cylinder etc.),
The roller 3 of the guide arm 4 is brought into contact with the cam profile of the arcuate cam 2 rotating with the cam shaft 1, and the guide arm shaft 5 attached to the cylinder head is used as a fulcrum shaft to obtain the action of the return spring 15 to move the guide arm 4 in the arrow direction. Roller 6 is made to reciprocate in the directions of B and C.
And the curved slipper follower 8 of the secondary arm 7
However, with the configuration conditions as shown in FIG. 2, a distance N from the center L of the guide arm shaft 5 to the outer circumference M of the roller 6 and a curved surface that becomes a circle at the center of L, and the secondary arm 7 has an arrow E.
When the slipper follower 8 slides back and forth from the point B to the point C by the roller 6 of the guide arm 4 with the guide arm shaft 5 as the fulcrum shaft, the main arm 1
1 and 11 are assembled in the cylinder head with the configuration of the arc cam 2, the guide arm 4, the compound arm, and the valve 12, which are set at a position where the main arm shaft 13 is not movable.
【００１１】[0011]
【発明の効果】 本発明では，従来の弁を押して戻すカ
ムプロファイル伝達方法を，往復接触摺動による弁への
カムリフト伝達を行うことで，従来の弁開閉でのジャン
プ・バウンス拳動の低減を図るとともに，複合アームで
の連続可変動弁機構による自在な可変伝達により，慣性
質量の増加や可変段階でのジャンプ・バウンス拳動の低
減が得られることで，自在な弁リフト量の可変を可能に
して，スロットルレス機構によるエンジンの全回転域で
の最適な燃焼を得て，ポンピングロスの低減，低速トル
クのアップと低燃費を図って，ＮＯｘの低減を図り，高
回転域では吸入効果を上げて高馬力を得るものである．According to the present invention, the conventional cam profile transmission method for pushing and returning the valve is performed by transmitting the cam lift to the valve by reciprocal contact sliding, thereby reducing the jump and bounce fist motion in the conventional valve opening and closing. At the same time, the variable variable transmission by the continuous variable valve mechanism in the compound arm enables the variable valve lift to be freely varied by increasing the inertial mass and reducing the jump and bounce fist at the variable stage. In addition, the throttleless mechanism achieves optimum combustion in all engine revolutions to reduce pumping loss, increase low-speed torque and fuel efficiency, and reduce NOx. It is the one that raises to obtain high horsepower.
【図１】往復摺動式・連続可変弁タイミング装置の分解
斜面図である．FIG. 1 is an exploded perspective view of a reciprocating sliding type continuously variable valve timing device.
【図２】本発明の往復接触摺動部の，ガイドアーム４と
湾曲したスリッパフォロア８の曲面の構成条件と，位置
設定を表した要約図である．FIG. 2 is a summary diagram showing the configuration conditions and the position setting of the curved surfaces of the guide arm 4 and the curved slipper follower 8 of the reciprocating contact sliding portion of the present invention.
【図３】図１の，セカンダリアーム７が，矢印Ｅの方向
に最大位置での，弁開閉停止状態となる，ガイドアーム
４と複合アームによる運動図である．FIG. 3 is a motion diagram of the guide arm 4 and the compound arm in FIG. 1 in which the secondary arm 7 is in the valve open / closed state at the maximum position in the direction of arrow E.
【図４】図１の，セカンダリアーム７が，矢印Ｄの方向
に最大位置での，弁最大開閉状態となる，ガイドアーム
４と複合アームによる運動図である．FIG. 4 is a motion diagram of the guide arm 4 and the compound arm in FIG. 1 in which the secondary arm 7 is in the valve maximum open / close state at the maximum position in the direction of arrow D.
【図５】図１の，セカンダリアーム７が，矢印ＤやＥの
方向に可動した時での，弁閉じ時期の弁閉じ安定となる
状態を表した図である．5 is a diagram showing a state in which the secondary arm 7 of FIG. 1 is stable in closing the valve at the valve closing timing when the secondary arm 7 is moved in the directions of arrows D and E. FIG.
【図６】本発明の，往復摺動開閉式でのガイドアーム可
動手段を，円弧カムより円滑に往復摺動が図れる，強制
的にガイドアーム可動を行った場合の参考図である．FIG. 6 is a reference diagram when the guide arm moving means of the reciprocating sliding open / close type according to the present invention is forcibly moved so that it can smoothly slide back and forth from the arc cam.
１ カムシャフト ２ 円弧カム ３ ローラー ４ ガイドアーム ５ ガイドアームシャフト ６ ローラー ７ セカンダリアーム ８ スリッパフォロア ９ 可変カム １０ セカンダリアーム １１ メインアーム １２ バルブ １３ メインアームシャフト １４ 止めピン １５ リターンスプリング １６ 可変リフト量 1 camshaft 2 arc cam 3 roller 4 guide arm 5 guide arm shaft 6 roller 7 secondary arm 8 slipper follower 9 variable cam 10 secondary arm 11 main arm 12 valve 13 main arm shaft 14 stop pin 15 return spring 16 variable lift amount
Claims (1)
と，ガイドアームシャフト５を軸に，円弧カム２のカム
プロファイルにそって押されて動くローラー３と，スリ
ッパフォロア８を押しながら動くローラー６を備えて一
体にしたガイドアーム４と，メインアーム１１，１１
を，セカンダリアーム７を有する連結軸セカンダリアー
ムシャフト１０で一対にして，回動軸メインアームシャ
フト１３に，可変カム９を止めビン１４で固定して一体
にした複合アームとで，構成することで，カムシャフト
１と一体で回転する円弧カム２のカム山で，ガイドアー
ムシャフト５を軸にローラー３によってガイドアーム４
の往復運動を得，複合アームの回動軸メインアームシャ
フト１３の回動で，可変カム９で，セカンダリアームシ
ャフト１０を軸にセカンダリアーム７を動かし，ガイド
アームシャフト５の中心から，湾曲したスリッパフォロ
ア８との接触距離を制御して，力点の変化を図る．ロー
ラー６とスリッパフォロア８との往復接触摺動による，
セカンダリアーム７を押して，戻る作用の働きで，セカ
ンダリアーム７は，可変カム９を支点にセカンダリアー
ムシャフト１０を押して，戻る，このことで，セカンダ
リアームシャフト１０に連結するメインアーム１１，１
１が，メインアームシャフト１３を軸に押され，戻り，
バルブ１２，１２に，円弧カム２のカムリフトを伝える
特徴で，弁リフト量の，弁停止から最大開閉までを連続
可変コントロールする，往復接触摺動開閉式・連続可変
弁タイミング装置．1. An arc cam 2 attached to a cam shaft 1.
, A roller 3 that is moved around the guide arm shaft 5 along the cam profile of the arcuate cam 2, a roller 6 that moves while pressing the slipper follower 8, and an integrated guide arm 4, and a main arm 11 , 11
By forming a pair with a connecting shaft secondary arm shaft 10 having a secondary arm 7 and a rotary cam main arm shaft 13 and a variable cam 9 fixed by a stopper bin 14 into a combined arm. , The cam lobe of the circular arc cam 2 that rotates integrally with the cam shaft 1, and the guide arm 4 by the roller 3 around the guide arm shaft 5
When the main arm shaft 13 rotates, the variable cam 9 moves the secondary arm 7 about the secondary arm shaft 10 to move the secondary arm 7 from the center of the guide arm shaft 5. The contact distance with the follower 8 is controlled to change the force point. By the reciprocating contact sliding of the roller 6 and the slipper follower 8,
By pushing the secondary arm 7 and returning it, the secondary arm 7 pushes the secondary arm shaft 10 around the variable cam 9 as a fulcrum and returns, whereby the main arms 11 and 1 connected to the secondary arm shaft 10 are returned.
1 is pushed around the main arm shaft 13 and returns,
A reciprocating contact sliding open / close type / continuous variable valve timing device that continuously controls the valve lift amount from valve stop to maximum opening / closing by the characteristic of transmitting the cam lift of the arc cam 2 to the valves 12, 12.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7083098A JPH08246824A (en) | 1995-03-04 | 1995-03-04 | Reciprocating contact sliding opening/closing and continuously variable valve timing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7083098A JPH08246824A (en) | 1995-03-04 | 1995-03-04 | Reciprocating contact sliding opening/closing and continuously variable valve timing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08246824A true JPH08246824A (en) | 1996-09-24 |
Family
ID=13792721
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7083098A Pending JPH08246824A (en) | 1995-03-04 | 1995-03-04 | Reciprocating contact sliding opening/closing and continuously variable valve timing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08246824A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005059320A1 (en) * | 2003-12-18 | 2005-06-30 | Toyota Jidosha Kabushiki Kaisha | Variable valve mechanism |
| JP2006070735A (en) * | 2004-08-31 | 2006-03-16 | Toyota Motor Corp | Variable valve train |
| CN100417787C (en) * | 2003-12-18 | 2008-09-10 | 丰田自动车株式会社 | Variable valve mechanism |
-
1995
- 1995-03-04 JP JP7083098A patent/JPH08246824A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005059320A1 (en) * | 2003-12-18 | 2005-06-30 | Toyota Jidosha Kabushiki Kaisha | Variable valve mechanism |
| CN100417787C (en) * | 2003-12-18 | 2008-09-10 | 丰田自动车株式会社 | Variable valve mechanism |
| US7424873B2 (en) | 2003-12-18 | 2008-09-16 | Toyota, Jidosha Kabushiki Kaisha | Variable valve mechanism |
| JP2006070735A (en) * | 2004-08-31 | 2006-03-16 | Toyota Motor Corp | Variable valve train |
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