JPH086569B2 - Valve train for internal combustion engine - Google Patents
Valve train for internal combustion engineInfo
- Publication number
- JPH086569B2 JPH086569B2 JP17428587A JP17428587A JPH086569B2 JP H086569 B2 JPH086569 B2 JP H086569B2 JP 17428587 A JP17428587 A JP 17428587A JP 17428587 A JP17428587 A JP 17428587A JP H086569 B2 JPH086569 B2 JP H086569B2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- plunger
- hydraulic pressure
- connection
- switching
- 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.)
- Expired - Fee Related
Links
Landscapes
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Description
【発明の詳細な説明】 A.発明の目的 （１） 産業上の利用分野 本発明は、少なくとも一部を吸気弁あるいは排気弁に
連動、連結した複数のカムフォロアが、カムシャフトの
回転に応じて作動すべく隣接配置され、各カムフォロア
には、各カムフォロアを一体に作動させるべく相互に連
結する連結状態とその連結状態を解除する連結解除状態
とを切換可能な連結切換機構が設けられる内燃機関の動
弁装置に関する。DETAILED DESCRIPTION OF THE INVENTION A. Purpose of the Invention (1) Field of Industrial Application The present invention is directed to a plurality of cam followers, at least a part of which is interlocked with and connected to an intake valve or an exhaust valve, according to the rotation of a camshaft. In the internal combustion engine, each cam follower is arranged adjacent to each other so as to operate, and each cam follower is provided with a connection switching mechanism capable of switching between a connected state in which the cam followers are connected to each other and a released state in which the connected state is released. The present invention relates to a valve train.
（２） 従来の技術 従来、かかる動弁装置は、たとえば特開昭61−19911
号公報により公知である。(2) Conventional Technology Conventionally, such a valve operating system has been disclosed in, for example, Japanese Patent Laid-Open No. 61-19911.
It is publicly known from Japanese Patent Publication No.
（３） 発明が解決しようとする課題 ところで上記従来のものでは、第１および第２カムフ
ォロアを連結可能な連結ピンと、第２および第３カムフ
ォロアを連結可能な連結ピンと、両連結ピンの移動を規
制するためのストッパピンとを同軸上で相互に当接させ
ておくとともに軸方向一方にばね付勢し、そのばね付勢
力に付ち勝つだけの高い油圧力を軸方向他方に作用させ
ることにより各ピンを連結作動せしめるようにしてい
る。而して、各ピンの連結および連結解除作動は可及的
速やかに行なわれる必要があるが、上記従来構造のよう
に連結解除作動を戻しばねで行うと、作動が比較的緩や
かとなり、連結解除が不円滑となることがある。(3) PROBLEMS TO BE SOLVED BY THE INVENTION In the above-mentioned conventional device, the connecting pin that can connect the first and second cam followers, the connecting pin that can connect the second and third cam followers, and the movement of both connecting pins are restricted. And the stopper pin for contacting each other on the same axis, and the spring is urged to one side in the axial direction, and a high hydraulic pressure to overcome the spring urging force is applied to the other side in the axial direction. Are designed to work together. Thus, the connection and disconnection operation of each pin needs to be performed as quickly as possible, but when the connection release operation is performed by the return spring as in the above-described conventional structure, the operation becomes relatively slow and the connection release May become unsmooth.
本発明は、かかる事情に鑑みてなされたものであり、
連結切換機構の連結および連結解除作動を可及的速やか
にして円滑な切換作動を可能とした内燃機関の動弁装置
を提供することを目的とする。The present invention has been made in view of such circumstances,
An object of the present invention is to provide a valve operating device for an internal combustion engine, which enables a smooth switching operation by connecting and disconnecting the connection switching mechanism as quickly as possible.
B.発明の構成 （１） 課題を解決するための手段 上記目的を達成するために本発明によれば、連結切換
機構は、各カムフォロアの配列方向に沿う一端のカムフ
ォロアに摺動可能に嵌合されるとともに複数のカムフォ
ロアを相互に連結する位置およびその連結を解除する位
置間で移動可能な第１プランジャと、前記配列方向に沿
う他端のカムフォロアに摺動可能に嵌合されるとともに
第１プランジャに連動された第２プランジャと、第１お
よび第２プランジャを連結位置側に付勢する油圧力を発
生すべく前記一端のカムフォロアおよび第１プランジャ
間に画成される第１油圧室と、第１および第２プランジ
ャを連結解除位置側に付勢する油圧力を発生すべく前記
他端のカムフォロアおよび第２プランジャ間に画成され
る第２油圧室とを備え、第１及び第２油圧室は、第２油
圧室に油圧を供給すると共に第１油圧室の油圧を解放す
る第１の切換状態と、第１油圧室に油圧を供給すると共
に第２油圧室の油圧を解放する第２の切換状態との二者
択一に切換可能な油圧供給源に接続され、第１及び第２
プランジャは、各油圧室に発生する油圧力によってのみ
前記連結位置および連結解除位置間を駆動される。B. Configuration of the Invention (1) Means for Solving the Problems In order to achieve the above object, according to the present invention, a connection switching mechanism is slidably fitted to a cam follower at one end along the arrangement direction of each cam follower. And a first plunger movable between a position for connecting a plurality of cam followers to each other and a position for releasing the connection, and a first plunger slidably fitted to a cam follower at the other end along the arrangement direction and a first A second plunger that is interlocked with the plunger; a first hydraulic chamber defined between the cam follower at the one end and the first plunger to generate hydraulic pressure that biases the first and second plungers toward the connecting position; A second hydraulic chamber defined between the cam follower at the other end and the second plunger to generate hydraulic pressure for urging the first and second plungers toward the connection release position; And the second hydraulic chamber supplies the hydraulic pressure to the second hydraulic chamber and releases the hydraulic pressure of the first hydraulic chamber in the first switching state, and supplies the hydraulic pressure to the first hydraulic chamber and the hydraulic pressure of the second hydraulic chamber. The first and second hydraulic pressure sources are connected to a hydraulic power supply source that can be switched to the second switching state to be released.
The plunger is driven between the connection position and the connection release position only by the hydraulic pressure generated in each hydraulic chamber.
（２） 作用 油圧供給源の二者択一的な切換作動によれば、第１及
び第２プランジャは互いに連動しながら、第１及び第２
油圧室のうちの何れか一室に択一的に作用する油圧にの
み応じてその油圧作用方向に作動するものであり、しか
もその何れか一室への油圧作用状態では他方の油圧室が
必ず油圧開放状態とされていて軸方向両端の油圧力の差
が大きく、そのため、それらプランジャを、軸方向一方
側および他方側の何れへも戻しばねに抵抗されずに大き
な駆動力で移動させることができる。このため、各プラ
ンジャを何れの切換方向にも迅速且つ強力に軸方向作動
させることができるようになり、各カムフォオアの連結
および連結解除の切替動作が何れも円滑且つ的確に行な
われる。(2) Operation According to the alternative switching operation of the hydraulic pressure supply source, the first and second plungers interlock with each other,
It operates in the direction of hydraulic pressure acting only on the hydraulic pressure that selectively acts on one of the hydraulic chambers, and when the hydraulic pressure is applied to any one of them, the other hydraulic chamber must be Since the hydraulic pressure is released and the difference between the hydraulic pressures at both ends in the axial direction is large, it is possible to move these plungers with a large driving force to both the one side and the other side in the axial direction without resisting the return spring. it can. Therefore, each plunger can be quickly and strongly actuated in any switching direction in the axial direction, and the switching operation for connecting and disconnecting each cam follower can be smoothly and accurately performed.
（３） 実施例 以下、図面により本発明の一実施例について説明する
と、先ず第１図および第２図において、機関本体Ｅに設
けられた一対の吸気弁1,1は、機関のクランク軸から1/2
の減速比で回転駆動されるカムシャフト２に一体的に設
けられた一対の低速用カム4,4および高速用カム５と、
カムシャフト２と平行なロッカシャフト６に枢支される
カムフォロアとしての第１、第２および第３ロッカアー
ム7,8,9と、各ロッカアーム7,8,9の連結および連結解除
を切換可能な連結切換機構10との働きにより開閉駆動さ
れる。(3) Embodiment Hereinafter, one embodiment of the present invention will be described with reference to the drawings. First, in FIG. 1 and FIG. 2, a pair of intake valves 1, 1 provided in an engine main body E includes a crankshaft of the engine. 1/2
A pair of low speed cams 4, 4 and a high speed cam 5 that are integrally provided on the cam shaft 2 that is rotationally driven at a reduction ratio of
First, second and third rocker arms 7,8,9 as cam followers pivotally supported by a rocker shaft 6 parallel to the camshaft 2, and a connection capable of switching connection and disconnection of each rocker arm 7,8,9. It is driven to open and close by the action of the switching mechanism 10.
カムシャフト２は、機関本体Ｅの上方で回転自在に配
設されており、低速用カム4,4は吸気弁1,1に対する位置
でカムシャフト２に一体化され、高速用カム５は両低速
用カム4,4間でカムシャフト２に一体化される。両低速
用カム4,4は、カムシャフト２の半径方向に沿う突出量
が比較的小さい高位部4aと、ベース円部4bとをそれぞれ
有し、高速用カム５は、カムシャフト２の半径方向に沿
う突出量が比較的大きい高位部5aと、ベース円部5bとを
有する。The camshaft 2 is rotatably arranged above the engine body E, the low speed cams 4, 4 are integrated with the camshaft 2 at a position relative to the intake valves 1, 1, and the high speed cam 5 is at both low speeds. It is integrated with the cam shaft 2 between the cams 4, 4. Both of the low speed cams 4, 4 have a high portion 4a with a relatively small protrusion amount along the radial direction of the camshaft 2 and a base circular portion 4b, and the high speed cam 5 has a radial direction of the camshaft 2. It has a high-order portion 5a having a relatively large amount of protrusion along and a base circular portion 5b.
ロッカシャフト６は、カムシャフト２よりも下方で固
定配置される。このロッカシャフト６には、第１〜第３
ロッカアーム７〜９がこの順に隣接してそれぞれ枢支さ
れるが、第１および第３ロッカアーム7,9は基本的に同
一形状に形成される。すなわち第１および第３ロッカア
ーム7,9は、吸気弁1,1に対応する位置でロッカシャフト
６にそれぞれ枢支され、各吸気弁1,1の上方位置まで延
設される。またおよび第３ロッカアーム7,9の上部には
低速用カム4,4に摺接するカムスリッパ11,12が設けられ
る。第２ロッカアーム８は、第１および第３ロッカアー
ム7,9間でロッカシャフト６に枢支されており、この第
２ロッカアーム８の上部には高速用カム５に摺接するカ
ムスリッパ13が設けられる。The rocker shaft 6 is fixedly arranged below the camshaft 2. The rocker shaft 6 includes the first to third parts.
The rocker arms 7 to 9 are pivotally supported adjacent to each other in this order, but the first and third rocker arms 7 and 9 are basically formed in the same shape. That is, the first and third rocker arms 7 and 9 are pivotally supported by the rocker shaft 6 at positions corresponding to the intake valves 1 and 1, and extend to positions above the intake valves 1 and 1. Further, cam slippers 11 and 12 which are in sliding contact with the low speed cams 4 and 4 are provided on the upper portions of the third rocker arms 7 and 9. The second rocker arm 8 is pivotally supported on the rocker shaft 6 between the first and third rocker arms 7 and 9, and a cam slipper 13 which is in sliding contact with the high speed cam 5 is provided on the upper portion of the second rocker arm 8.
各吸気弁1,1の上部には鍔部14がそれぞれ設けられて
おり、これらの鍔部14と機関本体Ｅとの間には弁ばね15
がそれぞれ介装される。したがって各吸気弁1,1は閉弁
方向すなわち上方に向けて付勢される。また第１および
第３ロッカアーム7,9には、各吸気弁1,1の上端に当接し
得るタペットねじ16が進退可能にそれぞれ螺合される。A flange portion 14 is provided above each intake valve 1, 1, and a valve spring 15 is provided between the flange portion 14 and the engine body E.
Are installed respectively. Therefore, the intake valves 1, 1 are urged in the valve closing direction, that is, upward. Further, tappet screws 16 capable of contacting the upper ends of the intake valves 1, 1 are respectively screwed to the first and third rocker arms 7, 9 so as to be able to advance and retract.
第３図を併せて参照して、第２ロッカアーム８の端部
下面には、有低円筒状のリフタ17が当接されており、こ
のリフタ17は機関本体Ｅとの間に介装したリフタばね18
により上方に付勢される。これにより第２ロッカアーム
８のカムスリッパ13は高速用カム５に常時摺接される。Referring also to FIG. 3, a lifter 17 having a lower and lower cylindrical shape is in contact with the lower surface of the end of the second rocker arm 8, and the lifter 17 is interposed between the lifter 17 and the engine body E. Spring 18
Is urged upward by. As a result, the cam slipper 13 of the second rocker arm 8 is always in sliding contact with the high speed cam 5.
第４図において、第１、第２および第３ロッカアーム
7,8,9には、それらの相対角変位を可能とする状態と、
それらを一体的に作動せしめる状態とを切換可能な連結
切換機構10が設けられる。In FIG. 4, first, second and third rocker arms
7,8,9 are the states that enable their relative angular displacement,
A connection switching mechanism (10) is provided which can switch between a state in which they are integrally operated.
連結切換機構10は、ロッカアーム７〜９の配列方向に
沿う一端のロッカアームすなわち第１ロッカアーム７に
摺動可能に嵌合させるとともに第１および第２ロッカア
ーム7,8を連結する位置およびその連結を解除する位置
間で移動可能な第１プランジャ22と、第１プランジャ22
の他端に一端を同軸に当接させて第２ロッカアーム８に
摺動可能に嵌合されるとともに第２および第３ロッカア
ーム8,9を連結する位置およびその連結を解除する位置
間で移動可能な連結ピン23と、連結ピン23の他端に一端
を同軸に当接させてロッカアーム７〜９の配列方向に沿
う他端のローカアームすなわち第３ロッカアーム９に摺
動可能に嵌合される第２プランジャ24と、第１プランジ
ャ22の一端および第１ロッカアー７間に画成される第１
油圧室21と、第２プランジャ24の他端及び第３ロッカア
ーム９間に画成される第２油圧室25とを備える。The connection switching mechanism 10 slidably fits to the rocker arm at one end along the arrangement direction of the rocker arms 7 to 9, that is, the first rocker arm 7, and releases the connection and the position at which the first and second rocker arms 7 and 8 are connected. And the first plunger 22 movable between the positions
One end is coaxially brought into contact with the other end of the second end and is slidably fitted to the second rocker arm 8 and movable between a position for connecting the second and third rocker arms 8 and 9 and a position for releasing the connection. Second connecting pin 23 and second end slidably fitted to the other end of the connecting pin 23 coaxially with the other end of the rocker arms 7 to 9 in the arrangement direction, that is, the third rocker arm 9. A first portion defined between the plunger 24 and one end of the first plunger 22 and the first rocker 7
A hydraulic chamber 21 and a second hydraulic chamber 25 defined between the other end of the second plunger 24 and the third rocker arm 9 are provided.
第１ロッカアーム７には、第２ロッカアーム８側に開
放した有底の第１摺動穴26がロッカシャフト６と平行に
して穿設され、この第１摺動穴26に第１プランジャ22が
摺動可能に嵌合され、第１プランジャ22の一端および第
１摺動穴26の閉塞端間に第１油圧室21が画成される。し
かも第１摺動穴26の途中には、第１プランジャ22の一端
を受けるべく第２ロッカアーム８側に臨んだ段部26aが
設けられており、第１プランジャ22の軸方向長さは、そ
の一端を段部26aに当接させたときにその他端が第１お
よび第２ロッカアーム7,8間にあるように設定される。The first rocker arm 7 is provided with a first sliding hole 26 having a bottom which is open to the second rocker arm 8 side in parallel with the rocker shaft 6, and the first plunger 22 is slid into the first sliding hole 26. The first hydraulic chamber 21 is movably fitted and defined between one end of the first plunger 22 and the closed end of the first sliding hole 26. Moreover, a step 26a facing the second rocker arm 8 side is provided in the middle of the first sliding hole 26 so as to receive one end of the first plunger 22, and the axial length of the first plunger 22 is The other end is set so as to be between the first and second rocker arms 7 and 8 when one end is brought into contact with the step portion 26a.
また第２ロッカアーム８には、第１摺動穴26と同径の
ガイド孔27がロッカシャフト６と平行して両側面間にわ
たって穿設される。このガイド孔27には連結ピン23が摺
動可能に嵌合されており、連結ピン23の軸方向長さは、
第１プランジャ22の他端に当接した一端が第１および第
２ロッカアーム7,8間にあるときに他端が第２および第
３ロッカアーム8,9間にあるように設定される。Further, a guide hole 27 having the same diameter as the first sliding hole 26 is formed in the second rocker arm 8 in parallel with the rocker shaft 6 between both side surfaces. The connecting pin 23 is slidably fitted in the guide hole 27, and the axial length of the connecting pin 23 is
The other end of the first plunger 22 is set so that it is between the first and second rocker arms 7 and 8 and the other end is between the second and third rocker arms 8 and 9.
第３ロッカアーム９には、第２ロッカアーム８側に開
放した有底の第２摺動穴28がロッカシャフト６と平行に
かつガイド孔27と同径にして穿設される。この第２摺動
穴28には、一端を連結ピン23の他端に当接させる第２プ
ランジャ24が摺動可能に嵌合され、第２摺動穴28の閉塞
端および第２プランジャ24の他端間に第２油圧室25が画
成される。しかも第２摺動穴28の途中には第２プランジ
ャ24の他端を受けるべく第２ロッカアーム８側に臨んだ
段部28aが設けられており、この段部28aに第２プランジ
ャ24の他端が当接したときに第２プランジャ24の一端は
第２摺動穴28内にある。In the third rocker arm 9, a bottomed second sliding hole 28 opened to the second rocker arm 8 side is bored in parallel with the rocker shaft 6 and with the same diameter as the guide hole 27. A second plunger 24, one end of which abuts on the other end of the connecting pin 23, is slidably fitted in the second sliding hole 28, and the closed end of the second sliding hole 28 and the second plunger 24 A second hydraulic chamber 25 is defined between the other ends. Moreover, a step portion 28a facing the second rocker arm 8 side is provided in the middle of the second sliding hole 28 so as to receive the other end of the second plunger 24, and the other end of the second plunger 24 is provided at this step portion 28a. The one end of the second plunger 24 is in the second sliding hole 28 when abutting against each other.
さらに第１摺動穴26、ガイド孔27および第２摺動穴28
は、各ロッカアーム7,8,9が、対応するカム4,5,4のベー
ス円部4b,5b,4bにそれぞれ摺接している状態で軸線を一
致させるようにして配置される。Further, the first sliding hole 26, the guide hole 27 and the second sliding hole 28
Are arranged so that the respective rocker arms 7, 8, 9 are in sliding contact with the base circle portions 4b, 5b, 4b of the corresponding cams 4, 5, 4 so that their axes coincide with each other.
ロッカシャフト６内には、第２ロッカーアーム８に対
応する部分に設けられた隔壁29により２分割されて第１
油圧供給路31および第２油圧供給路32が形成される。第
１ロッカアーム７には、第１油圧室21に通じる油路33
と、その油路33に連通してロッカシャフト６を囲繞する
環状溝34とが設けられ、ロッカシャフト６には第１油圧
供給路31を環状溝34に連通せしめる油孔35が穿設され
る。また第３ロッカアーム９には、第２油圧室25に通じ
る油路36と、その油路36に連通してロッカシャフト６を
囲繞する環状溝37とが設けられ、ロッカシャフト６には
第２油圧供給路32を環状溝37に連通せしめる油孔38が穿
設される。したがって第１油圧供給路31は第１油圧室21
に常時連通し、第２油圧供給路32は第２油圧室25に常時
連通する。The rocker shaft 6 is divided into two parts by a partition wall 29 provided in a portion corresponding to the second rocker arm 8.
A hydraulic pressure supply passage 31 and a second hydraulic pressure supply passage 32 are formed. The first rocker arm 7 has an oil passage 33 leading to the first hydraulic chamber 21.
And an annular groove 34 that communicates with the oil passage 33 and surrounds the rocker shaft 6, and an oil hole 35 that allows the first hydraulic pressure supply passage 31 to communicate with the annular groove 34 is formed in the rocker shaft 6. . Further, the third rocker arm 9 is provided with an oil passage 36 communicating with the second hydraulic chamber 25, and an annular groove 37 communicating with the oil passage 36 and surrounding the rocker shaft 6, and the rocker shaft 6 is provided with the second hydraulic pressure. An oil hole 38 is formed to connect the supply passage 32 to the annular groove 37. Therefore, the first hydraulic pressure supply passage 31 is connected to the first hydraulic pressure chamber 21.
The second hydraulic pressure supply passage 32 always communicates with the second hydraulic pressure chamber 25.
第１および第２油圧供給路31,32は、第２油圧室25に
油圧を供給すると共に第１油圧室21の油圧を解放する第
１の切換状態と、第１油圧室21に油圧を供給すると共に
第２油圧室25の油圧を解放する第２の切換状態と二者択
一に切換可能な油圧供給源40に接続される。この油圧供
給源40は、油タンク41から油を汲上げる油圧ポンプ42
と、その油圧ポンプ42の油圧を択一的に切換えて第１お
よび第２油圧供給路31,32に交互に供給するための切換
弁43とを有する。油圧ポンプ42の吐出口には、その上流
側から順にリリーフ弁44および逆止弁45が備えられた供
給路46が接続される。また切換弁43は、油タンク41に通
じる解放路47を第１油圧供給路31に通じる第１接続路48
に連通せしめると共に前記供給路46を第２油圧供給路32
に通じる第２接続路49に連通せしめる第１切換位置と、
供給路46を第１接続路48に連通せしめると共に第２接続
路49を解放路47に連通せしめる第２切替位置とを切替可
能な電磁切換弁であり、この電磁切換弁43が前記第１切
換位置にある時が油圧供給源40の第１の切換状態に対応
し、また同弁43が前記第２切換位置にある時が同供給源
40の第２の切換状態に対応する。前記電磁切換弁43の切
換作動はコンピュータ等の制御手段50により制御され
る。The first and second hydraulic pressure supply passages 31 and 32 supply the hydraulic pressure to the second hydraulic chamber 25 and the first switching state in which the hydraulic pressure in the first hydraulic chamber 21 is released, and supply the hydraulic pressure to the first hydraulic chamber 21. At the same time, it is connected to a hydraulic pressure supply source 40 that can be switched to a second switching state in which the hydraulic pressure in the second hydraulic chamber 25 is released. The hydraulic pressure source 40 is a hydraulic pump 42 that pumps oil from an oil tank 41.
And a switching valve 43 for selectively switching the hydraulic pressure of the hydraulic pump 42 and alternately supplying the hydraulic pressure to the first and second hydraulic pressure supply passages 31, 32. A supply passage 46 having a relief valve 44 and a check valve 45 in this order from the upstream side is connected to the discharge port of the hydraulic pump 42. The switching valve 43 also includes a first connection passage 48 that connects an open passage 47 that communicates with the oil tank 41 to the first hydraulic pressure supply passage 31.
And the supply passage 46 is connected to the second hydraulic pressure supply passage 32.
A first switching position for communicating with the second connection path 49 leading to
An electromagnetic switching valve that can switch between a second switching position that allows the supply path 46 to communicate with the first connection path 48 and a second connection path 49 that communicates with the release path 47. This electromagnetic switching valve 43 is the first switching When in the position, the hydraulic pressure source 40 corresponds to the first switching state, and when the valve 43 is in the second switching position, the hydraulic source 40 has the same switching state.
Corresponds to the second switching state of 40. The switching operation of the electromagnetic switching valve 43 is controlled by the control means 50 such as a computer.
制御手段50には、機関の冷却水温を検出する検出器S
1、機関回転数を検出する検出器S2、スロットル開度を
検出する検出器S3および機関の吸気負圧を検出する検出
器S4等が接続されており、制御手段50は、それらの検出
器S1〜S4からの信号に基づいて、機関が低速運転状態で
あると判断したときには切換弁43を第１切換位置とし、
機関が高速運転状態にあると判断したときには切換弁43
を第２切換位置に切換える。The control means 50 includes a detector S for detecting the cooling water temperature of the engine.
1, a detector S2 for detecting the engine speed, a detector S3 for detecting the throttle opening, a detector S4 for detecting the intake negative pressure of the engine, etc. are connected, the control means 50, those detectors S1 Based on the signals from S4 to S4, when it is determined that the engine is operating at low speed, the switching valve 43 is set to the first switching position,
When it is judged that the engine is operating at high speed, the switching valve 43
To the second switching position.
次にこの実施例の作用について説明すると、機関の低
速運転時には、制御手段50により切換弁43が第１切換位
置となる。このため油圧ポンプ42からの油圧は供給路4
6、第２接続路49、第２油圧供給路32、油孔38、環状溝3
7および油路36を経て第２油圧室25に供給される。また
第１油圧室21は、油路33、環状溝34、油孔35、第１油圧
供給路31、第１接続路48および解放路47を介してタンク
41に連通される。このため連結切換機構10においては、
第２油圧室25に作用している油圧により第１プランジャ
22、連結ピン23および第２プランジャ24が第１油圧室21
側に押圧されており、第１プランジャ22および連結ピン
23の当接面は第１および第２ロッカアーム7,8間にあ
り、連結ピン23および第２プランジャ24の当接面は第２
および第３ロッカアーム8,9間にある。したがって各ロ
ッカアーム７〜９は連結解除状態にあり、第１および第
３ロッカアーム7,9が低速用カム4,4により揺動作動する
のに応じて両吸気弁1,1が低速用カム4,4の形状に対応し
たタイミングおよびリフト量で開閉作動する。Next, the operation of this embodiment will be described. During the low speed operation of the engine, the control means 50 causes the switching valve 43 to be in the first switching position. Therefore, the hydraulic pressure from the hydraulic pump 42 is supplied to the supply path 4
6, second connection path 49, second hydraulic pressure supply path 32, oil hole 38, annular groove 3
It is supplied to the second hydraulic chamber 25 via 7 and the oil passage 36. The first hydraulic chamber 21 is connected to the tank via the oil passage 33, the annular groove 34, the oil hole 35, the first hydraulic pressure supply passage 31, the first connection passage 48 and the release passage 47.
Connected to 41. Therefore, in the connection switching mechanism 10,
The first plunger is driven by the hydraulic pressure acting on the second hydraulic chamber 25.
22, the connecting pin 23 and the second plunger 24 are the first hydraulic chamber 21.
Is pushed to the side, the first plunger 22 and the connecting pin
The contact surface of 23 is between the first and second rocker arms 7 and 8, and the contact surface of the connecting pin 23 and the second plunger 24 is the second surface.
And between the third rocker arms 8 and 9. Therefore, the respective rocker arms 7 to 9 are in the uncoupled state, and both intake valves 1 and 1 are driven by the low speed cams 4 and 4 in response to the first and third rocker arms 7 and 9 swinging by the low speed cams 4 and 4. It opens and closes at the timing and lift amount corresponding to the shape of 4.
機関の高速運転時には、制御手段50により切換弁43が
第２切換位置となる。このため、第２油圧室25に通じる
第２接続路49が開放路47に連通されるとともに、第１油
圧室21に通じる第１接続路48が油圧ポンプ42に接続さ
れ、第２油圧室25の油圧が解放されるとともに第１油圧
室21に油圧が供給される。これにより軸方向に相互に当
接した第１プランジャ22、連結ピン23および第２プラン
ジャ24は、第２油圧室25側に速やかに移動し、第１プラ
ンジャ22がガイド孔27に嵌合して第１および第ロッカア
ーム7,8が連結されるとともに、連結ピン23が第２摺動
穴28に嵌合して第２および第３ロッカアーム8,9が連結
される。このようにして、全てのロッカアーム７〜９が
一体的に連結されることになり、全てのロッカアーム７
〜９が高速用カム５で揺動駆動され、両吸気弁1,1が高
速用カム５の形状に応じたタイミングおよびリフト量で
開閉作動する。During high speed operation of the engine, the switching valve 43 is set to the second switching position by the control means 50. Therefore, the second connection passage 49 communicating with the second hydraulic chamber 25 is communicated with the open passage 47, the first connection passage 48 communicating with the first hydraulic chamber 21 is connected with the hydraulic pump 42, and the second hydraulic chamber 25 Is released and the oil pressure is supplied to the first oil pressure chamber 21. As a result, the first plunger 22, the connecting pin 23 and the second plunger 24, which are in mutual contact with each other in the axial direction, quickly move to the second hydraulic chamber 25 side, and the first plunger 22 is fitted into the guide hole 27. The first and third rocker arms 7 and 8 are connected, and the connecting pin 23 is fitted into the second sliding hole 28 to connect the second and third rocker arms 8 and 9. In this way, all the rocker arms 7 to 9 are integrally connected, and all the rocker arms 7 to 9 are connected.
9 to 9 are oscillated by the high speed cam 5, and both intake valves 1 and 1 are opened and closed at a timing and a lift amount according to the shape of the high speed cam 5.
本発明の他の実施例として、第１および第３ロッカア
ーム7,9の少なくとも一方を、機関の低速運転時に休止
させるようにしてもよい。すなわち低速用カム4,4の少
なくとも一方を、ロッカシャフト６の軸線を中心とする
円形でロッカシャフト６に設けた隆起部に代えてもよ
い。As another embodiment of the present invention, at least one of the first and third rocker arms 7 and 9 may be stopped during low speed operation of the engine. That is, at least one of the low-speed cams 4, 4 may be replaced by a raised portion provided on the rocker shaft 6 in a circular shape centered on the axis of the rocker shaft 6.
また本発明は、３つのカムフォロアで２つの吸気弁を
駆動するようにした動弁装置だけでなく、相互に隣接し
た一対のカムフォロアで２つあるいは１つの吸気弁を駆
動するようにした動弁装置についても適用可能であり、
この場合には、第１および第２プランジャが相互に当接
される。Further, the present invention is not limited to a valve operating device in which two intake valves are driven by three cam followers, and a valve operating device in which two or one intake valve is driven by a pair of adjacent cam followers. Is also applicable,
In this case, the first and second plungers abut against each other.
以上の実施例では吸気弁の動弁装置について述べた
が、本発明を排気弁の動弁装置に適用することも可能で
ある。Although the valve operating device for the intake valve has been described in the above embodiments, the present invention can be applied to the valve operating device for the exhaust valve.
C.発明の効果 以上のように本発明によれば、カムフォロア配列方向
一端側のカムフォロアとこれに嵌合する第１プランジャ
との間に第１油圧室が、またその他端側のカムフォロア
とこれに嵌合する第２プランジャとの間に第２油圧室が
それぞれ画成され、それら第１および第２油圧室は、第
２油圧室に油圧を供給すると共に第１油圧室の油圧を解
放する第１の切換状態と、第１油圧室と油圧を供給する
と共に第２油圧室の油圧を解放する第２の切換状態との
二者択一に切換可能な油圧供給源に接続され、第１およ
び第２プランジャは、各油圧室に発生する油圧力によっ
てのみ前記連結位置および連結解除位置間を駆動される
ので、第１及び第２プランジャは互いに連動しながら、
第１及び第２油圧室のうちの何れか一室に択一的に作用
する油圧にのみ応じてその油圧作用方向に移動し、しか
もその何れか一室への油圧作用状態では他方の油圧室が
必ず油圧解放状態とされていて軸方向両端での油圧力の
差が大きいことから、それらプランジャを、軸方向一方
向側および他方側の何れへも戻しばねに抵抗されずに大
きな駆動力で移動させることができ、その結果、各プラ
ンジャを何れの切換方向にも迅速且つ強力に作動させる
ことができて、カムフォロアの連結および連結解除を何
れも円滑且つ的確に切換えることができるから、機関運
転状態に合わせて連結切換機構の切換動作を常にタイミ
ングよく行うことが可能となる。C. Effect of the Invention As described above, according to the present invention, the first hydraulic chamber is provided between the cam follower on one end side in the cam follower arrangement direction and the first plunger fitted thereto, and the cam follower on the other end side and the cam follower are provided on the other end side. Second hydraulic chambers are respectively defined between the second hydraulic chambers and the second plungers, and the first and second hydraulic chambers supply hydraulic pressure to the second hydraulic chambers and release hydraulic pressures of the first hydraulic chambers. Connected to a hydraulic pressure supply source capable of switching between a switching state of No. 1 and a second switching state of supplying hydraulic pressure to the first hydraulic chamber and releasing hydraulic pressure of the second hydraulic chamber. Since the second plunger is driven between the connection position and the connection release position only by the hydraulic pressure generated in each hydraulic chamber, the first and second plungers interlock with each other,
It moves in the hydraulic action direction only in response to the hydraulic pressure that selectively acts on one of the first and second hydraulic chambers, and the other hydraulic chamber is in the hydraulic action state on any one of the first and second hydraulic chambers. Is always in the hydraulic release state, and the difference in hydraulic pressure at both ends in the axial direction is large.Therefore, with a large driving force, these plungers are not resisted by the return spring in either the axial one direction side or the other side. As a result, the plungers can be quickly and strongly actuated in any switching direction, and the cam followers can be connected and disconnected smoothly and accurately. It is possible to always perform the switching operation of the connection switching mechanism in good timing according to the state.
また各プランジャが各油圧室に発生する油圧力によっ
てのみ連結位置及び連結解除位置間を駆動される関係
で、各プランジャに対する戻しばねが省略可能となるか
ら、それだけ構造の簡素化が図られると共に、プランジ
ャ駆動のために必要な油圧を極力軽減することができ
る。更に前記油圧供給源は、第１及び第２油圧室への油
圧供給（解放）を二者択一に行うため、油圧の給排制御
を極力簡素化できるばかりか、各プランジャの位置が不
定となってしまう事態の回避に有効である。Moreover, since the return spring for each plunger can be omitted because each plunger is driven between the connection position and the connection release position only by the hydraulic pressure generated in each hydraulic chamber, the structure can be simplified accordingly. The hydraulic pressure required to drive the plunger can be reduced as much as possible. Further, since the hydraulic pressure supply source selectively supplies (releases) the hydraulic pressure to the first and second hydraulic chambers, the hydraulic pressure supply / discharge control can be simplified as much as possible, and the positions of the plungers are not fixed. It is effective in avoiding the situation that becomes.
図面は本発明の一実施例を示すもので、第１図は平面
図、第２図は第１図のII−II線断面図、第３図は第１図
のIII−III線断面図、第４図は第２図のIV−IV線に沿う
断面および油圧系統を示す図である。 １……吸気弁、２……カムシャフト、7,8,9……カムフ
ォロアとしてのロッカアーム、10……連結切換機構、21
……第１油圧室、22……第１プランジャ、24……第２プ
ランジャ、25……第２油圧室、40……油圧供給源The drawings show an embodiment of the present invention. FIG. 1 is a plan view, FIG. 2 is a sectional view taken along line II-II in FIG. 1, and FIG. 3 is a sectional view taken along line III-III in FIG. FIG. 4 is a view showing a cross section taken along line IV-IV in FIG. 2 and a hydraulic system. 1 ... intake valve, 2 ... camshaft, 7,8,9 ... rocker arm as cam follower, 10 ... coupling switching mechanism, 21
...... First hydraulic chamber, 22 ...... First plunger, 24 ...... Second plunger, 25 ...... Second hydraulic chamber, 40 ...... Hydraulic supply source
Claims (1)
気弁に連動、連結した複数のカムフォロア（７〜９）
が、カムシャフト（２）の回転に応じて作動すべく隣接
配置され、各カムフォロア（７〜９）には、各カムフォ
ロア（７〜９）を一体に作動させるべく相互に連結する
連結状態とその連結状態を解除する連結解除状態とを切
換可能な連結切換機構（10）が設けられてなる、内燃機
関の動弁装置において、 連結切換機構（10）は、各カムフォロア（７〜９）の配
列方向に沿う一端のカムフォロア（７）に摺動可能に嵌
合されるとともに複数のカムフォロア（７〜９）を相互
に連結する位置およびその連結を解除する位置間で移動
可能な第１プランジャ（22）と、前記配列方向に沿う他
端のカムフォロア（９）に摺動可能に嵌合されるととも
に第１プランジャ（22）に連動された第２プランジャ
（24）と、第１および第２プランジャ（22,24）を連結
位置側に付勢する油圧力を発生すべく前記一端のカムフ
ォロア（７）および第１プランジャ（22）間に画成され
る第１油圧室（21）と、第１および第２プランジャ（2
2,24）を連結解除位置側に付勢する油圧力を発生すべく
前記他端のカムフォロア（９）および第２プランジャ
（24）間に画成される第２油圧室（25）とを備え、 第１及び第２油圧室（21,25）は、第２油圧室（25）に
油圧を供給すると共に第１油圧室（21）の油圧を解放す
る第１の切換状態と、第１油圧室（21）に油圧を供給す
ると共に第２油圧室（25）の油圧を解放する第２の切換
状態との二者択一に切換可能な油圧供給源（40）に接続
され、 第１及び第２プランジャ（22,24）は、各油圧室（21,2
5）に発生する油圧力によってのみ前記連結位置および
連結解除位置間を駆動されることを特徴とする、内燃機
関の動弁装置。1. A plurality of cam followers (7-9), at least a part of which is interlocked with and linked to an intake valve (1) or an exhaust valve.
Are arranged adjacent to each other so as to operate in accordance with the rotation of the camshaft (2), and the respective cam followers (7-9) are connected to each other so as to integrally operate the respective cam followers (7-9). In a valve operating system for an internal combustion engine, which is provided with a connection switching mechanism (10) capable of switching between a connection released state and a connection released state, the connection switching mechanism (10) includes an array of cam followers (7-9). A first plunger (22) slidably fitted to a cam follower (7) at one end along the direction and movable between a position where a plurality of cam followers (7 to 9) are connected to each other and a position where the connection is released. ), A second plunger (24) slidably fitted to the cam follower (9) at the other end along the arrangement direction and interlocked with the first plunger (22), and the first and second plungers (). 22,24) are connected A first hydraulic chamber (21) defined between the cam follower (7) and the first plunger (22) at the one end to generate an oil pressure for urging the first and second plungers (2).
A second hydraulic chamber (25) defined between the cam follower (9) at the other end and the second plunger (24) so as to generate an oil pressure for urging the second and the second plungers (24) toward the disconnection position side. , The first and second hydraulic chambers (21, 25) supply the hydraulic pressure to the second hydraulic chamber (25) and release the hydraulic pressure of the first hydraulic chamber (21), It is connected to a hydraulic pressure supply source (40) capable of switching between a second switching state of supplying hydraulic pressure to the chamber (21) and releasing the hydraulic pressure of the second hydraulic chamber (25), and The second plunger (22, 24) is connected to each hydraulic chamber (21, 2
A valve train for an internal combustion engine, which is driven between the connection position and the connection release position only by the hydraulic pressure generated in 5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17428587A JPH086569B2 (en) | 1987-07-13 | 1987-07-13 | Valve train for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17428587A JPH086569B2 (en) | 1987-07-13 | 1987-07-13 | Valve train for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6419103A JPS6419103A (en) | 1989-01-23 |
| JPH086569B2 true JPH086569B2 (en) | 1996-01-24 |
Family
ID=15975998
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17428587A Expired - Fee Related JPH086569B2 (en) | 1987-07-13 | 1987-07-13 | Valve train for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH086569B2 (en) |
Cited By (2)
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|---|---|---|---|---|
| WO2016052731A1 (en) * | 2014-10-03 | 2016-04-07 | ヤマハ発動機株式会社 | Valve gear for engine |
| WO2016052729A1 (en) * | 2014-10-03 | 2016-04-07 | ヤマハ発動機株式会社 | Valve gear for engine and method for producing rocker arm |
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| WO1993023891A1 (en) * | 1992-05-19 | 1993-11-25 | Martin Marietta Corporation | Rf-transparent antenna sunshield membrane |
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| EP2381074A1 (en) * | 2010-04-20 | 2011-10-26 | Kwang Yang Motor Co., Ltd. | Variable valve lift mechanism for engine and arrangement of oil control valve |
| JP5996882B2 (en) * | 2012-02-20 | 2016-09-21 | 株式会社オティックス | Variable valve mechanism and operating method of internal combustion engine |
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Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60192203U (en) * | 1984-05-30 | 1985-12-20 | 三菱自動車工業株式会社 | Valve control device for engine valve system |
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1987
- 1987-07-13 JP JP17428587A patent/JPH086569B2/en not_active Expired - Fee Related
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| WO2016052731A1 (en) * | 2014-10-03 | 2016-04-07 | ヤマハ発動機株式会社 | Valve gear for engine |
| WO2016052729A1 (en) * | 2014-10-03 | 2016-04-07 | ヤマハ発動機株式会社 | Valve gear for engine and method for producing rocker arm |
| JPWO2016052731A1 (en) * | 2014-10-03 | 2017-06-15 | ヤマハ発動機株式会社 | Engine valve gear |
| JPWO2016052729A1 (en) * | 2014-10-03 | 2017-06-22 | ヤマハ発動機株式会社 | Engine valve gear and rocker arm manufacturing method |
| US10167744B2 (en) | 2014-10-03 | 2019-01-01 | Yamaha Hatsudoki Kabushiki Kaisha | Valve gear for engine |
| US10215063B2 (en) | 2014-10-03 | 2019-02-26 | Yamaha Hatsudoki Kabushiki Kaisha | Valve gear for engine and method of manufacturing rocker arms |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6419103A (en) | 1989-01-23 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |