JPH02271018A - Valve operating device of engine - Google Patents
Valve operating device of engineInfo
- Publication number
- JPH02271018A JPH02271018A JP9207689A JP9207689A JPH02271018A JP H02271018 A JPH02271018 A JP H02271018A JP 9207689 A JP9207689 A JP 9207689A JP 9207689 A JP9207689 A JP 9207689A JP H02271018 A JPH02271018 A JP H02271018A
- Authority
- JP
- Japan
- Prior art keywords
- cam member
- plunger
- plate cam
- camshaft
- cylinder
- 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
- 230000008878 coupling Effects 0.000 abstract description 3
- 238000010168 coupling process Methods 0.000 abstract description 3
- 238000005859 coupling reaction Methods 0.000 abstract description 3
- 238000000034 method Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
Landscapes
- Valve Device For Special Equipments (AREA)
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
この発明はエンジンの弁作f!h装置、待に1つの吸気
弁または排気弁に対して設けられたカムプロフィールの
異なるカム部材を、運忙条件に応じて選択的に作動させ
、これによって弁作動の制御を行うものに関する。[Detailed Description of the Invention] (Industrial Application Field) This invention provides an engine valve f! The present invention relates to a device that selectively operates cam members with different cam profiles provided for one intake valve or exhaust valve depending on busy conditions, thereby controlling valve operation.
(従来の技術)
従来からエンジンの燃費性能および出力性能等を向上さ
せる目的で運転状態に応じて、吸気弁および排気弁の作
動を制御し、これによって吸排気のタイミングあるいは
吸排気量を制御することが知られている(特開昭62−
131.、907号公報参照)。(Prior art) Conventionally, in order to improve the fuel efficiency and output performance of an engine, the operation of intake valves and exhaust valves is controlled depending on the operating condition, and thereby the timing of intake and exhaust or the amount of intake and exhaust is controlled. It is known that
131. , No. 907).
これを第6図で説明すると、図示のものは直接駆動方式
のオーバーへラドカムの例で、カムシャフト2にはエン
ジンの低回転時と高回転時にそれぞれ適したプロフィー
ルを有する板カム部材3゜4が取り付けられる。このう
ち、低速用の板カム部材3がカムシャフト2に対して固
定されるのに対し、高速用の板カム部材4は、カムシャ
フト2に対して回動自在に取り付けられ、後述する連結
機構が作動した場合にカムシャフト2に固定される。な
お、この板カム部材4は係止ピン5によりカムシャフト
2の軸方向へは動き得ないようになっている。To explain this with reference to Fig. 6, the one shown is an example of a direct drive type overdrive cam, and the camshaft 2 is equipped with a plate cam member 3°4 having a profile suitable for low and high engine speeds. can be installed. Of these, the plate cam member 3 for low speeds is fixed to the camshaft 2, whereas the plate cam member 4 for high speeds is rotatably attached to the camshaft 2, and has a connection mechanism described later. is fixed to the camshaft 2 when the camshaft is activated. The plate cam member 4 is prevented from moving in the axial direction of the camshaft 2 by a locking pin 5.
カムシャフト2と板カム部材4との間には、第7図で示
すように、カムシャフト2の半径方向内側に向かう円筒
状のシリンダ2Aと、このシリンダ2Aを摺動しシリン
ダ2Aの深さと略同じ長さを有するプランジャ6と、こ
のプランジャ6およ1シリンダ2Aにて画成される油圧
室7と、前記シリンダ2Aよりも若干大きな径を有しカ
ムシャフト2の半径方向外側に向かって穿設された円部
状の嵌合孔8と、この孔8を摺動し得るスプリング受け
つと、スプリング受け9を介し前記プランジャ6をカム
シャフト2の側に付勢するスプリング10とからなる連
結8!構が構成され、油圧室7に油圧が導入されていな
い場合は、スプリング10によりシリンダ2A内へと押
し戻されるためにプランジャ6が嵌合孔8にはまり込め
ず、板カム部材4がカムシャフト2に連結されていない
。この場合、弁1は低速用板カム部材3にしたがって9
7トされ、この板カム部材3よれば、比較的開弁期間の
短いあるいは弁リフトの小さな特性が得られる。As shown in FIG. 7, between the camshaft 2 and the plate cam member 4, there is a cylindrical cylinder 2A that faces inward in the radial direction of the camshaft 2. A plunger 6 having approximately the same length, a hydraulic chamber 7 defined by the plunger 6 and one cylinder 2A, and a hydraulic chamber 7 having a slightly larger diameter than the cylinder 2A toward the outside in the radial direction of the camshaft 2. A connection consisting of a circular fitting hole 8, a spring receiver that can slide in the hole 8, and a spring 10 that biases the plunger 6 toward the camshaft 2 via the spring receiver 9. 8! If the mechanism is configured and hydraulic pressure is not introduced into the hydraulic chamber 7, the plunger 6 will not fit into the fitting hole 8 because it will be pushed back into the cylinder 2A by the spring 10, and the plate cam member 4 will not fit into the camshaft 2. not connected to. In this case, the valve 1 is 9 in accordance with the plate cam member 3 for low speed.
According to this plate cam member 3, characteristics such as a relatively short valve opening period or a small valve lift can be obtained.
一方、エンジンの高回転時に、オイルポンプ15からの
油圧が電磁弁16を介して油圧室7に導入されると、ス
プリング10の弾性力に抗して、プランジャ6が嵌合孔
8のトレーリング側に形成された助走溝11に摺接しつ
つ移動して嵌合孔8にはまり、これにて板カム部材4と
カムシャフト2が連結される。ここに、板カム部材4は
、他方の板カム部材3に比して、開弁期間が長くあるい
は弁リフト量が大きくなるようにカムノーズ部を形成し
であるので、画板カム部材3.4がバルブリフター(あ
るいはタペット)12と摺接しつつ回転すると、低速用
の板カム部材3がバルブリフター12より浮き上がり、
この場合の弁リフト特性は高j玉用の板カム部材4にし
たがう。On the other hand, when the oil pressure from the oil pump 15 is introduced into the hydraulic chamber 7 via the electromagnetic valve 16 during high rotation of the engine, the plunger 6 moves against the elastic force of the spring 10 and moves into the trailing position of the fitting hole 8. The plate cam member 4 and the camshaft 2 are connected to each other by slidingly moving into the running groove 11 formed on the side and fitting into the fitting hole 8 . Here, the plate cam member 4 has a cam nose portion formed so that the valve opening period is longer or the valve lift amount is larger than that of the other plate cam member 3. When rotating while slidingly contacting the valve lifter (or tappet) 12, the low speed plate cam member 3 rises above the valve lifter 12,
The valve lift characteristics in this case follow the plate cam member 4 for high j balls.
(発明が解決しようとする課題)
このような装置では、プランジャ6がカムシャフト22
の半径方向に摺動するよう設けられているため、高回転
時の弁リフトに際してプランジャ6を嵌合孔8にはまり
込ませた状態で保持させておくには高い油圧が必要とな
る。これは、板カムに加わる荷重のうちカムシャフト2
の軸芯に向かう分力が、プランジャ6をシリンダ2Aへ
と押し戻すように、つまり高速用板カム部材4のカムシ
ャフト2への連結を解くように働くので、この分力に対
抗できるだけの油圧が必要となるからである。(Problem to be Solved by the Invention) In such a device, the plunger 6 is connected to the camshaft 22.
Since the plunger 6 is provided to slide in the radial direction of the valve, high oil pressure is required to keep the plunger 6 fitted in the fitting hole 8 when the valve is lifted at high rotation speeds. Of the load applied to the plate cam, the camshaft 2
The component force directed toward the axis of the cylinder acts to push the plunger 6 back toward the cylinder 2A, that is, to disconnect the high-speed plate cam member 4 from the camshaft 2, so that the hydraulic pressure is sufficient to counter this component force. This is because it is necessary.
たとえば、板カムには1.00kg以上の大きな荷重が
その周面に加わるが、いま仮に100kgとし、これが
そのままプランジャ6に加わったとすれば、この場合に
プランジャ6(その径を81とする)に作用する圧力P
を計算してみると、
(π/4)Xo、82 XP=100
より、P=200kg/cm2となり、極めて高い値と
なるのである。For example, a large load of 1.00 kg or more is applied to the circumferential surface of a plate cam, but if the load is 100 kg and is directly applied to the plunger 6, in this case the plunger 6 (its diameter is 81) will be Acting pressure P
When calculated, (π/4)Xo, 82 XP=100, P=200kg/cm2, which is an extremely high value.
また、エンジン回献数が高くなるのに応じて板カムに加
わる荷重も大きくなるので、上記油圧もその分高くしな
ければならない。Furthermore, as the number of revolutions of the engine increases, the load applied to the plate cam also increases, so the oil pressure must be increased accordingly.
この発明はこのような従来の課題に着目してなされたも
ので、板カムに作用する大きな荷重が連結8!構の作動
に影響を与えることがないように、かつ連結のための時
間も短くなるようにする装置を提供することを目的とす
る。This invention was made by focusing on such conventional problems, and the large load acting on the plate cam is caused by the connection 8! It is an object of the present invention to provide a device that does not affect the operation of the structure and also reduces the time required for connection.
(9題を解決するための手段)
この発明は、低速用のプロフィールを有する板カム部材
をカムシャフトに固定するとともに、高速用のプロフィ
−ルを有する板カム部材をカムシャフトの回転方向に回
動自在に設ける一方で、前記カムシャフトと平行に低速
用板カム部材に穿設され高速用板カム部材と対向する側
面に開口するシリンダと、このシリンダを摺動可能でシ
リンダの深さと略同じ長さを有するプランジャと、この
プランジャおよびシリンダにて画成される作動圧力室と
、前記カムシャフトと平行にかつ前記シリンダに対向す
る位置から高速用カム部材に穿設されシリンダとほぼ同
じ径を有する嵌合孔と、この孔を摺動し得るスプリング
受けと、スプリング受けを介し前記プランジャを低速用
板カム部材の側に付勢するスプリングとからなる連結機
構を構成し、エンジンの高回転時に前記作動圧力室に作
動圧力を導くとともに、前記嵌合孔の開口する高速用板
カム部材側面にカムシャフトの軸芯から嵌合孔までの距
離を半径とする円弧状のかつ嵌合孔に向けて徐々に深く
なる溝を設けた。(Means for Solving Problems 9) This invention fixes a plate cam member having a low-speed profile to a camshaft, and rotates the plate cam member having a high-speed profile in the rotational direction of the camshaft. A cylinder is provided to be movable, and a cylinder is bored in the low-speed plate cam member parallel to the camshaft and opens on the side facing the high-speed plate cam member, and the cylinder is slidable and has a depth approximately equal to the depth of the cylinder. a plunger having a long length, an operating pressure chamber defined by the plunger and the cylinder, and a hole bored in the high-speed cam member from a position parallel to the camshaft and facing the cylinder and having a diameter substantially the same as that of the cylinder. A coupling mechanism is constructed of a fitting hole, a spring receiver that can slide in this hole, and a spring that biases the plunger toward the low-speed plate cam member through the spring receiver. While guiding the working pressure to the working pressure chamber, a circular arc-shaped fitting hole whose radius is the distance from the axis of the camshaft to the fitting hole is directed to the side surface of the high-speed plate cam member where the fitting hole opens. A groove was created that gradually became deeper.
(作用)
エンジンの高回転時には、プランジャが嵌合孔にはまり
込むことにより低速用と高速用の画板カム部材が一体に
連結される。(Function) When the engine rotates at high speed, the plunger fits into the fitting hole, so that the low-speed and high-speed drawing plate cam members are integrally connected.
この場合、プランジャの摺動する方向がカムシャフトと
平行であるため、弁リフトに伴い高速用板カム部材に作
用する荷重のすべてが、プランジャを剪断する荷重とし
て作用し、プランジャをシリンダへと押し戻す方向に加
わることがない。In this case, since the sliding direction of the plunger is parallel to the camshaft, the entire load that acts on the high-speed plate cam member due to the valve lift acts as a load that shears the plunger, pushing the plunger back into the cylinder. There is no direction involved.
また、連結に際してプランジャの摺動する部位がイ茨合
札に向けて徐々に深くなる溝とされであることから、プ
ランジャがこの溝に圧接した状態では、プランジャを溝
へと押す力の分力がプランジャを嵌合孔へと向かわせる
方向に作用する。In addition, since the part where the plunger slides during connection is a groove that gradually deepens toward the thorn tag, when the plunger is in pressure contact with this groove, the component of the force that pushes the plunger into the groove is acts in a direction to move the plunger toward the fitting hole.
(実施例)
第1図は直接駆動方式のオーバーへラドカムの例で、同
図において弁(吸気弁、排気弁のいずれでも良い)のす
ぐ真上に位置してカムブラケット(図示せず)に軸支さ
れるカムシャフト22には、エンジンの低回転時と高回
転時にそれぞれ適したプロフィールを有する板カム部材
23.24が取り付けられる。(Example) Figure 1 shows an example of a direct drive type overdrive cam. Plate cam members 23 and 24 having profiles suitable for low engine speed and high engine speed are attached to the supported camshaft 22, respectively.
このうち、低速用の板カム部材23がカムシャフト22
に固定されるのに対し、高速用の板カム部材24につい
てはカムシャフト22の回転方向に対して回動自在に設
けられる。詳しくは、板カム部材24の内周面24Aの
径をカムシャフト22の外周面22Aよりも若干大きく
形成するとともに、板カム部材24の右側面24Bとそ
の右方に位置するカムブラケットの開のカムシャフト上
に、円筒状のカムガイドカラー25を介在させることに
より、カムシャフト22の軸方向に動き得ないようにす
るのである。Of these, the plate cam member 23 for low speed is attached to the camshaft 22.
On the other hand, the plate cam member 24 for high speed use is rotatably provided in the rotational direction of the camshaft 22. Specifically, the diameter of the inner circumferential surface 24A of the plate cam member 24 is formed to be slightly larger than the outer circumferential surface 22A of the camshaft 22, and the diameter of the right side surface 24B of the plate cam member 24 and the opening of the cam bracket located to the right thereof are By interposing the cylindrical cam guide collar 25 on the camshaft, the camshaft 22 is prevented from moving in the axial direction.
画板カム部材23.24の間には、これらを−体に連結
することのできる機構が、カムシャフト22と平行な方
向でかつカムシャフト22の軸芯より所定の距離離れた
位置に構成される。これは、低速用の板カム部材23の
右側面23Aよりカムシ+7 ) 22と平行に穿設さ
れる円筒状のシリンダ31と、このシリンダ31を摺動
しシリンダ31の深さと略同じ長さを有するプランジャ
32と、このプランジャ32およゾシリンダ31にて画
成される油圧室(作動圧力室)33と、高速用の板カム
部材24の左側面24. Cにおいて前記シリンダ31
に対向する位置からカムシャフト22と平行に穿設され
、′シリンダ31とほぼ同じ径の大径部34Aを有する
段付きの嵌合孔34と、この嵌合孔34の小径部34B
を摺動し得るスプリング受け35と、スプリング受け3
5を介し前記プランジャ32を低速用の板カム部材23
の側に付勢するスプリング36とからなり、油圧室33
に油圧(作動圧力)が導入されていない場合は、スプリ
ング36によりシリンダ31内へと押し戻されるために
プランジャ32が嵌合孔大径部34Aにはまり込めず、
高速用の板カム部材24が低速用の板カム部材23に連
結されていない。Between the drawing board cam members 23 and 24, a mechanism capable of connecting these to the body is constructed in a direction parallel to the camshaft 22 and at a position a predetermined distance away from the axis of the camshaft 22. . This consists of a cylindrical cylinder 31 that is drilled from the right side surface 23A of the low-speed plate cam member 23 in parallel with the camshaft 22, and a cylinder 31 that slides on this cylinder 31 and has a length that is approximately the same as the depth of the cylinder 31. a plunger 32, a hydraulic chamber (operating pressure chamber) 33 defined by the plunger 32 and the cylinder 31, and a left side surface 24 of the high-speed plate cam member 24. At C, the cylinder 31
A stepped fitting hole 34 is bored parallel to the camshaft 22 from a position facing the camshaft 22 and has a large diameter portion 34A having approximately the same diameter as the cylinder 31, and a small diameter portion 34B of this fitting hole 34.
a spring receiver 35 on which the spring receiver 3 can slide;
5, the plunger 32 is connected to the plate cam member 23 for low speed.
The hydraulic chamber 33
If hydraulic pressure (operating pressure) is not introduced into the cylinder 31, the plunger 32 cannot fit into the large diameter portion 34A of the fitting hole because it is pushed back into the cylinder 31 by the spring 36.
The plate cam member 24 for high speed is not connected to the plate cam member 23 for low speed.
一方、エンジンの高回転時に、オイルポンプがらの油圧
が矢印のようにカムシャフト22内に設けた油圧通路4
1.油供給孔429円筒状の連絡孔43、通路44を介
して油圧室33に導入されると、スプリング36の弾性
力に抗して、プランジャ32が嵌合孔大径部34Aには
まり、これにて画板カム部材23.24が一体に連結さ
れる。On the other hand, when the engine rotates at high speeds, the oil pressure from the oil pump flows through the hydraulic passage 4 provided in the camshaft 22 as shown by the arrow.
1. When the oil supply hole 429 is introduced into the hydraulic chamber 33 through the cylindrical communication hole 43 and the passage 44, the plunger 32 is fitted into the large diameter portion 34A of the fitting hole against the elastic force of the spring 36. The drawing board cam members 23 and 24 are integrally connected.
なお、プランジャ32とスプリング受け35との互いに
当接する側には面取りがなされ、また嵌合孔大径部34
Aの開口端と、嵌合孔大径部34Aと嵌合孔小径部34
Bの間にはテーパ一部が設けられている。37はストッ
パーである。Note that the sides of the plunger 32 and the spring receiver 35 that contact each other are chamfered, and the large diameter portion 34 of the fitting hole is chamfered.
The opening end of A, the large diameter part 34A of the fitting hole, and the small diameter part 34 of the fitting hole
A portion of the taper is provided between B. 37 is a stopper.
第2図は高速用の板カム部材24をfIfJ1図におい
て左方から見た斜視図で、その側面24Cにはカムシャ
フト22の軸芯から嵌合孔34までの距離を半径とする
円弧状の溝51が所定の角度範囲にわたって設けられる
。第3図はこの溝51に沿ってyl、開した断面図(第
2図のA−A#X断面図)で、嵌合孔34に向かって徐
々に深くなるテーパー状の溝として形成している。32
図において、嵌合(L34を中心として図示のように溝
51を反時計方向に設けるかあるいは時計方向に設ける
かは、カムシャフト22の回転方向とこのカムシャフト
22の軸方向における2つの板カム部材23,24の相
対位置関係に応じて定まる。FIG. 2 is a perspective view of the high-speed plate cam member 24 seen from the left in FIG. A groove 51 is provided over a predetermined angular range. FIG. 3 is a cross-sectional view (A-A#X cross-sectional view of FIG. 2) opened along this groove 51, which is formed as a tapered groove that gradually deepens toward the fitting hole 34. There is. 32
In the figure, whether the groove 51 is provided counterclockwise or clockwise as shown in the figure with L34 as the center depends on the rotational direction of the camshaft 22 and the axial direction of the camshaft 22 between the two plate cams. It is determined depending on the relative positional relationship between the members 23 and 24.
ここに、溝51はプランジャ32の案内溝として設けら
れるもので、テーパー状に限るものでなく、第4図と第
5図に示すように階段状やなめからな曲線状の溝52.
53としても構わない。Here, the groove 51 is provided as a guide groove for the plunger 32, and is not limited to a tapered shape, but may be a stepped or smooth curved groove 52, as shown in FIGS. 4 and 5.
53 is also acceptable.
ここで、この実施例の作用を説明すると、エンジンの高
回転時には、プランジャ32が嵌合孔大径部34Aには
まり込むことにより画板カム部材23.24が一体に連
結される。Here, the operation of this embodiment will be explained. When the engine rotates at high speed, the plunger 32 fits into the large diameter portion 34A of the fitting hole, so that the drawing plate cam members 23 and 24 are integrally connected.
この場合、プランジャ32の摺動する方向がカムシャフ
ト22と平行であるため、弁リフトに伴い高速用板カム
部材24に作用する荷重は、そのすべてがプランジャ3
2を剪断する荷重として作用する。つまり、プランジャ
32をシリンダ31へと押し戻す方向に加わることがな
く、これはエンジン回転数が高くなっても同じである。In this case, since the sliding direction of the plunger 32 is parallel to the camshaft 22, all of the load acting on the high-speed plate cam member 24 due to the valve lift is transferred to the plunger 32.
2 acts as a shearing load. In other words, no force is applied to push the plunger 32 back into the cylinder 31, and this is true even when the engine speed increases.
このため、油圧室33に導入する油圧は、プランジャ3
2の応答速度の7αからだけで決定すればよく、したが
って3〜4kg/cm2もあれば十分て・あると考えら
れる。Therefore, the hydraulic pressure introduced into the hydraulic chamber 33 is
It is sufficient to determine it only from 7α of the response speed of 2, and therefore 3 to 4 kg/cm2 is considered to be sufficient.
また、テーパー状の溝51を設けであることより、プラ
ンジャ32が溝51に圧接した状態では、プランジャ3
2を溝51へと押す力の分力がプランジャ32を嵌合孔
34へと向かわせる方向に作用するので、この分力にて
プランジャ32が3棄やかに嵌合孔34へと導かれ、連
結されるまでの時間が短くされる。これに対して、溝5
1を設けていないと、画板カム部材23.24がMJN
的に回動してシリンダ31と嵌合孔大径部34Aとが真
正面で出会うのを待つしがないので、連結されるまでの
時間が長引くことがあるのである。Further, since the tapered groove 51 is provided, when the plunger 32 is in pressure contact with the groove 51, the plunger 3
Since the component force of the force pushing 2 into the groove 51 acts in the direction of directing the plunger 32 toward the fitting hole 34, this component force causes the plunger 32 to be guided 3 unwillingly into the fitting hole 34. , the time it takes to connect is shortened. On the other hand, groove 5
If 1 is not provided, the drawing board cam members 23 and 24 will be MJN.
Since there is no choice but to wait until the cylinder 31 and the large diameter portion 34A of the fitting hole meet directly in front of each other, it may take a long time to connect them.
ii後に、実施例では、直接駆動方式について説明した
が、ロッカーアーム式に対しても適用することができる
。また、画板カム部材23.24の連結に際して、油圧
をもって駆動する方式に限らず、吸入負圧や電動にて駆
動する方式とすることもできる。After ii, in the embodiments, a direct drive system has been described, but it can also be applied to a rocker arm system. Further, when connecting the drawing plate cam members 23, 24, the method is not limited to the method of driving using hydraulic pressure, but it is also possible to use a method of driving using suction negative pressure or electric power.
(発明の効果)
この発明は、低速用のプロフィールを有する板カム部材
をカムシャフトに固定するとともに、高速用のプロフィ
ールを有する板カム部材をカムシャフトの回転方向に回
動自在に設ける一方で、エンジンの高回転時に、作動圧
力を利用してプランジャを嵌合孔にはまり込ませること
に上り画板カム部材を一体に連結することのできるfi
lを画板カム部材の開でカムシャフトと平行な方向に構
成するとともに、前記嵌合孔の開口する高速用板カム部
材側面にカムシャフトの軸芯から嵌合孔までの距離を半
径とする円弧状のかつ嵌合孔に向けて徐々に深くなる溝
を設けたため、連結のだめの作動圧力が小さく済むばか
りか、連結までの時間を短縮することができる。(Effects of the Invention) The present invention fixes a plate cam member having a profile for low speed to a camshaft, and provides a plate cam member having a profile for high speed so as to be rotatable in the rotational direction of the camshaft. When the engine rotates at high speed, the plunger is fitted into the fitting hole using operating pressure, and the drawing board cam member can be integrally connected.
l is formed in a direction parallel to the camshaft when the drawing plate cam member opens, and a circle whose radius is the distance from the axis of the camshaft to the fitting hole is formed on the side surface of the high speed plate cam member where the fitting hole opens. Since the groove is arc-shaped and gradually deepens toward the fitting hole, not only the operating pressure of the connection stopper can be reduced, but also the time required for connection can be shortened.
第1図はこの発明の一実施例の断面図、fJS2図はこ
の実施例の高速用板カム部材24の斜視図、第3図は第
2図のA−Ai断面図、第4図と第5図はそれぞれ第3
図に対応する池の実施例のA−A#i!断面図、!@6
図は従来装置のエンジンの部分断面図、第7図は従来装
置の連結部の詳細図である。
22・・・カムシャフト、23・・・低速用の板カム部
材、24・・・高速用の板カム部材、31・・・シリン
ダ、32・・・プランジャ、33・・・油圧室(作動圧
力室)、34・・・嵌合孔、34A・・・嵌合孔大径部
、35・・・スプリング受け、36・・・スプリング、
51〜53・・・溝。
特許出願人 日産自動車株式会社第1図
j6−−−スフ゛リンク゛
第2図
ス1
24第3図
ロー
24第4図1 is a sectional view of an embodiment of the present invention, FIG. Figure 5 is the third
A-A#i of the pond embodiment corresponding to the figure! Cross section! @6
The figure is a partial sectional view of the engine of the conventional device, and FIG. 7 is a detailed view of the connecting portion of the conventional device. 22... Camshaft, 23... Plate cam member for low speed, 24... Plate cam member for high speed, 31... Cylinder, 32... Plunger, 33... Hydraulic chamber (operating pressure chamber), 34... Fitting hole, 34A... Fitting hole large diameter part, 35... Spring receiver, 36... Spring,
51-53...Groove. Patent Applicant: Nissan Motor Co., Ltd. Figure 1 j6 --- Link Figure 2 S1 24 Figure 3 Row 24 Figure 4
Claims (1)
トに固定するとともに、高速用のプロフィールを有する
板カム部材をカムシャフトの回転方向に回動自在に設け
る一方で、前記カムシャフトと平行に低速用板カム部材
に穿設され高速用板カム部材と対向する側面に開口する
シリンダと、このシリンダを摺動可能でシリンダの深さ
と略同じ長さを有するプランジャと、このプランジャお
よびシリンダにて画成される作動圧力室と、前記カムシ
ャフトと平行にかつ前記シリンダに対向する位置から高
速用カム部材に穿設されシリンダとほぼ同じ径を有する
嵌合孔と、この孔を摺動し得るスプリング受けと、スプ
リング受けを介し前記プランジャを低速用板カム部材の
側に付勢するスプリングとからなる連結機構を構成し、
エンジンの高回転時に前記作動圧力室に作動圧力を導く
とともに、前記嵌合孔の開口する高速用板カム部材側面
にカムシャフトの軸芯から嵌合孔までの距離を半径とす
る円弧状のかつ嵌合孔に向けて徐々に深くなる溝を設け
たことを特徴とするエンジンの弁作動装置。A plate cam member having a profile for low speeds is fixed to the camshaft, and a plate cam member having a profile for high speeds is rotatably provided in the rotational direction of the camshaft, while a plate cam member for low speeds is fixed to the camshaft in parallel with the camshaft. A cylinder that is bored in the cam member and opens on the side facing the high-speed plate cam member, a plunger that is slidable on the cylinder and has a length that is approximately the same as the depth of the cylinder, and is defined by the plunger and the cylinder. a fitting hole bored in the high-speed cam member from a position parallel to the camshaft and facing the cylinder and having approximately the same diameter as the cylinder; and a spring receiver that can slide in the hole. , and a spring that biases the plunger toward the low-speed plate cam member through a spring receiver,
In addition to guiding the working pressure to the working pressure chamber during high rotation of the engine, an arc-shaped groove whose radius is the distance from the axis of the camshaft to the fitting hole is formed on the side surface of the high-speed plate cam member where the fitting hole opens. A valve operating device for an engine, characterized in that a groove is provided that gradually becomes deeper toward a fitting hole.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9207689A JPH02271018A (en) | 1989-04-12 | 1989-04-12 | Valve operating device of engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9207689A JPH02271018A (en) | 1989-04-12 | 1989-04-12 | Valve operating device of engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH02271018A true JPH02271018A (en) | 1990-11-06 |
Family
ID=14044362
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP9207689A Pending JPH02271018A (en) | 1989-04-12 | 1989-04-12 | Valve operating device of engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH02271018A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015183655A (en) * | 2014-03-26 | 2015-10-22 | 富士重工業株式会社 | High-pressure pump structure of internal combustion engine |
-
1989
- 1989-04-12 JP JP9207689A patent/JPH02271018A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015183655A (en) * | 2014-03-26 | 2015-10-22 | 富士重工業株式会社 | High-pressure pump structure of internal combustion engine |
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