JPH04214915A - Hydraulic driving device of engine valve for internal combustion engine - Google Patents
Hydraulic driving device of engine valve for internal combustion engineInfo
- Publication number
- JPH04214915A JPH04214915A JP3028692A JP2869291A JPH04214915A JP H04214915 A JPH04214915 A JP H04214915A JP 3028692 A JP3028692 A JP 3028692A JP 2869291 A JP2869291 A JP 2869291A JP H04214915 A JPH04214915 A JP H04214915A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- damper chamber
- engine
- hydraulic pressure
- cylinder body
- 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
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 8
- 239000003921 oil Substances 0.000 claims description 27
- 239000010720 hydraulic oil Substances 0.000 claims description 15
- 238000005192 partition Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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、上端を閉塞したシリン
ダ孔が固定のシリンダ体に設けられ、該シリンダ孔には
、閉弁方向にばね付勢された機関弁に下端部が連動、連
結されるとともにシリンダ孔の上部閉塞端との間にダン
パ室を形成する弁駆動ピストンが摺動可能に嵌合され、
機関弁の開弁時期に対応して油圧を発生する油圧発生手
段と前記ダンパ室との間には、前記油圧発生手段からダ
ンパ室への作動油の流通のみを許容するチェック弁と、
固定オリフィスとが介設され、シリンダ体には、弁駆動
ピストンが機関弁の全閉状態から所定距離以上開弁方向
に移動したときにダンパ室に連通すべくシリンダ孔の内
面に開口する油路が油圧発生手段に常時連通して設けら
れる内燃機関用機関弁の油圧駆動装置に関する。[Industrial Application Field] The present invention provides a fixed cylinder body with a cylinder hole whose upper end is closed, and whose lower end is interlocked and connected to an engine valve that is spring-biased in the valve-closing direction. and a valve driving piston is slidably fitted to form a damper chamber between the cylinder hole and the upper closed end of the cylinder hole;
a check valve that allows only flow of hydraulic oil from the hydraulic pressure generating means to the damper chamber, between the hydraulic pressure generating means that generates hydraulic pressure corresponding to the opening timing of the engine valve and the damper chamber;
A fixed orifice is interposed, and the cylinder body has an oil passage that opens on the inner surface of the cylinder hole to communicate with the damper chamber when the valve driving piston moves in the valve opening direction from the fully closed state of the engine valve by a predetermined distance or more. The present invention relates to a hydraulic drive device for an engine valve for an internal combustion engine, which is provided in constant communication with a hydraulic pressure generating means.
【０００２】0002
【従来の技術】従来、かかる装置は、たとえば特開平１
−２５３５１５号公報等により知られており、機関弁の
開弁時には油圧発生手段で発生した油圧をチェック弁お
よび固定オリフィスを介してダンパ室に作用させ、その
ダンパ室の油圧により弁駆動ピストンを押圧して機関弁
を開弁作動せしめ、機関弁の閉弁時にはその着座直前に
おいて、ダンパ室から油圧発生手段側への作動油の流通
を固定オリフィスで絞ることにより機関弁の閉弁速度を
緩やかにし、着座時の衝撃を緩和して機関弁の損傷を防
止するようにしている。2. Description of the Related Art Conventionally, such a device has been used, for example, in Japanese Unexamined Patent Publication No.
This is known from Publication No. 253515, etc., and when the engine valve is opened, the hydraulic pressure generated by the hydraulic pressure generating means is applied to the damper chamber through the check valve and the fixed orifice, and the valve driving piston is pushed by the hydraulic pressure in the damper chamber. When the engine valve closes, just before it is seated, the flow of hydraulic oil from the damper chamber to the hydraulic pressure generating means is throttled with a fixed orifice, thereby slowing down the closing speed of the engine valve. , to prevent damage to the engine valve by alleviating the impact when sitting on the seat.
【０００３】0003
【発明が解決しようとする課題】ところが、上記従来の
ものでは、油圧発生手段に連通してシリンダ孔の内面に
設けられた油路よりも上方でかつシリンダ孔の上部閉塞
端よりも下方位置でシリンダ体に固定オリフィスが設け
られている。このため、機関弁の全閉状態で弁駆動ピス
トンの上端を臨ませたダンパ室に、作動油に混入したエ
アーが溜まるおそれがあり、そのようなエアー溜が生じ
ると、高圧が作用するダンパ室の剛性が低下し、機関弁
の開弁リフト量が低下したり、所定時期以前に機関弁の
ジャンプが生じたりして、機関弁の円滑な作動が損なわ
れるおそれがある。[Problems to be Solved by the Invention] However, in the above-mentioned conventional device, it is necessary to prevent the oil from being removed at a position above the oil passage provided on the inner surface of the cylinder hole and communicating with the hydraulic pressure generating means, and below the upper closed end of the cylinder hole. A fixed orifice is provided in the cylinder body. For this reason, when the engine valve is fully closed, there is a risk that air mixed in with the hydraulic oil may accumulate in the damper chamber facing the upper end of the valve drive piston. There is a risk that the rigidity of the engine valve will decrease, the opening lift amount of the engine valve will decrease, or the engine valve will jump before a predetermined time, which may impair the smooth operation of the engine valve.
【０００４】本発明は、かかる事情に鑑みてなされたも
のであり、ダンパ室にエアーが溜まることを防止して機
関弁の円滑な作動を確保し得るようにした内燃機関用機
関弁の油圧駆動装置を提供することを目的とする。The present invention has been made in view of the above circumstances, and provides a hydraulically driven engine valve for an internal combustion engine that prevents air from accumulating in the damper chamber and ensures smooth operation of the engine valve. The purpose is to provide equipment.
【０００５】[0005]
【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、固定オリフィスは、ダンパ室の上
端に連通してシリンダ体に設けられる。According to the present invention, a fixed orifice is provided in the cylinder body and communicates with the upper end of the damper chamber.
【０００６】[0006]
【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。DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings.
【０００７】図１〜図４は本発明の一実施例を示すもの
であり、図１は全体縦断側面図、図２は図１の要部拡大
縦断面図、図３は弁駆動ピストンの拡大斜視図、図４は
弁リフト特性線図である。1 to 4 show one embodiment of the present invention, FIG. 1 is an overall vertical sectional side view, FIG. 2 is an enlarged vertical sectional view of the main part of FIG. 1, and FIG. 3 is an enlarged view of the valve driving piston. The perspective view of FIG. 4 is a valve lift characteristic diagram.
【０００８】先ず図１において、内燃機関のシリンダヘ
ッドＨには、機関本体を共働して構成するシリンダブロ
ック（図示せず）との間に形成される燃焼室１の天井面
に開口する吸気弁口２が吸気ポート３に連通して穿設さ
れており、該吸気弁口２に固設されたリング状弁座部材
４に着座可能な機関弁としての吸気弁５が、シリンダヘ
ッドＨに設けられたガイド筒６により吸気弁口２を開閉
すべく上下移動自在に案内される。しかも吸気弁５の上
端部に設けられた鍔部５ａとシリンダヘッドＨとの間に
は弁ばね７が縮設されており、この弁ばね７のばね力に
より吸気弁５は上方すなわち閉弁方向に向けてばね付勢
されている。First, in FIG. 1, the cylinder head H of an internal combustion engine has an intake air opening at the ceiling surface of a combustion chamber 1 formed between the cylinder block (not shown) which together constitutes the engine body. A valve port 2 is bored to communicate with an intake port 3, and an intake valve 5 as an engine valve that can be seated on a ring-shaped valve seat member 4 fixed to the intake valve port 2 is attached to the cylinder head H. A guide cylinder 6 provided guides the intake valve port 2 so as to be vertically movable to open and close it. Moreover, a valve spring 7 is compressed between the flange 5a provided at the upper end of the intake valve 5 and the cylinder head H, and the spring force of the valve spring 7 causes the intake valve 5 to move upward, that is, in the valve closing direction. It is spring biased towards.
【０００９】一方、シリンダヘッドＨの上方には、図示
しないクランク軸により回転駆動されるカムシャフト８
が配設されており、このカムシャフト８に設けられたカ
ム９を含む油圧発生手段１０が、カム９のプロフィルに
応じて吸気弁５を開閉駆動するための油圧を発生すべく
吸気弁５の上方に配設される。On the other hand, above the cylinder head H, a camshaft 8 is rotatably driven by a crankshaft (not shown).
A hydraulic pressure generating means 10 including a cam 9 provided on the camshaft 8 generates hydraulic pressure for opening and closing the intake valve 5 according to the profile of the cam 9. placed above.
【００１０】図２において、油圧発生手段１０は、前記
カム９と、吸気弁５の上方位置で固定の支持部１１に固
設されるシリンダ体１２と、前記カム９に摺接するとと
もに支持部１１の上部に摺動可能に嵌合されるリフタ１
４と、該リフタ１４に上端を当接させてシリンダ体１２
の上部に摺動可能に嵌合されるカム従動ピストン１５と
を備える。しかも支持部１１はシリンダヘッドＨに固設
されるものである。In FIG. 2, the hydraulic pressure generating means 10 includes the cam 9, a cylinder body 12 fixed to a fixed support part 11 at a position above the intake valve 5, and a cylinder body 12 that is in sliding contact with the cam 9 and the support part 11. Lifter 1 slidably fitted to the top of the
4, and the cylinder body 12 with its upper end in contact with the lifter 14.
The cam driven piston 15 is slidably fitted to the upper part of the cam driven piston 15. Furthermore, the support portion 11 is fixed to the cylinder head H.
【００１１】吸気弁５の上方で支持部１１には、上方か
ら順に、第１孔部１８、第１孔部１８よりも小径であっ
て段部１９を介して第１孔部１８の下端に連なる第２孔
部２０、ならびに第２孔部２０よりも大径であって段部
２１を介して第２孔部２０の下端に連なる第３孔部２２
が吸気弁５と同軸に上下に延びて穿設される。Above the intake valve 5, the supporting part 11 has, in order from the top, a first hole 18, which has a diameter smaller than the first hole 18 and is connected to the lower end of the first hole 18 via a stepped part 19. A continuous second hole 20, and a third hole 22 that has a larger diameter than the second hole 20 and continues to the lower end of the second hole 20 via a step 21.
is bored and extends vertically coaxially with the intake valve 5.
【００１２】シリンダ体１２は、第２孔部２０に挿通し
得る程度の小径部１２ａと、第３孔部２２に嵌合し得る
程度の大径部１２ｂとを上方に臨む段部１２ｃを介して
同軸に連設して基本的に円筒状に形成される。該シリン
ダ体１２の大径部１２ｂは、その段部１２ｃと、前記段
部２１との間にシム２７を介在せしめながら小径部１２
ａを第２孔部２０に挿通するようにして第３孔部２２に
嵌合される。しかも小径部１２ａの第２孔部２０よりも
上方に突出した部分には雄ねじ２９が刻設されており、
この雄ねじ２９に螺合するナット３０を段部１９に当接
するまで締付けることによりシリンダ体１２が支持部１
１に固定される。またシリンダ体１２における大径部１
２ｂの外面には第３孔部２２の内面との間のシールを果
たすべく環状のシール部材３１が嵌着される。The cylinder body 12 has a small diameter portion 12a large enough to be inserted into the second hole 20 and a large diameter portion 12b large enough to fit into the third hole 22 through a stepped portion 12c facing upward. They are coaxially connected and basically formed into a cylindrical shape. The large diameter portion 12b of the cylinder body 12 is connected to the small diameter portion 12 with a shim 27 interposed between the stepped portion 12c and the stepped portion 21.
a is inserted into the second hole 20 and fitted into the third hole 22 . Moreover, a male thread 29 is carved in a portion of the small diameter portion 12a that protrudes above the second hole portion 20.
By tightening the nut 30 screwed onto this male screw 29 until it abuts against the stepped portion 19, the cylinder body 12 is attached to the support portion 1.
Fixed to 1. Also, the large diameter portion 1 in the cylinder body 12
An annular sealing member 31 is fitted onto the outer surface of the third hole 2b to provide a seal with the inner surface of the third hole 22.
【００１３】シリンダ体１２の中間部には、該シリンダ
体１２内を下部シリンダ孔３３と上部シリンダ孔３４と
に仕切る仕切壁３２が設けられており、カム従動ピスト
ン１５は、該仕切壁３２との間に油圧発生室４０を画成
して上部シリンダ孔３４に摺動可能に嵌合される。また
吸気弁５の上端すなわち開弁方向２５に沿う後端に当接
する弁駆動ピストン１３が下部シリンダ孔３３の上部閉
塞端すなわち前記仕切壁３２との間にダンパ室３９を画
成して下部シリンダ孔３３に摺動可能に嵌合される。A partition wall 32 is provided in the middle of the cylinder body 12 to partition the inside of the cylinder body 12 into a lower cylinder hole 33 and an upper cylinder hole 34, and the cam driven piston 15 is connected to the partition wall 32. A hydraulic pressure generation chamber 40 is defined between the upper cylinder hole 34 and the upper cylinder hole 34 is slidably fitted. Further, the valve driving piston 13 that abuts the upper end of the intake valve 5, that is, the rear end along the valve opening direction 25, defines a damper chamber 39 between the upper closed end of the lower cylinder hole 33, that is, the partition wall 32, and the lower cylinder It is slidably fitted into the hole 33.
【００１４】シリンダ体１２における下部シリンダ孔３
３の途中には、弁駆動ピストン１３の外面との間に環状
油路３５を形成する環状凹部３６が設けられる。またシ
リンダ体１２には、第３孔部２２の内面と共働して油路
３７を形成するための加工が施され、この油路３７は環
状油路３５および油圧発生室４０間を連通する。Lower cylinder hole 3 in cylinder body 12
3 is provided with an annular recess 36 that forms an annular oil passage 35 with the outer surface of the valve drive piston 13. Further, the cylinder body 12 is processed to form an oil passage 37 in cooperation with the inner surface of the third hole 22, and this oil passage 37 communicates between the annular oil passage 35 and the oil pressure generation chamber 40. .
【００１５】弁駆動ピストン１３には、油圧発生室４０
からダンパ室３９への作動油の流通のみを許容するチェ
ック弁４１が設けられる。このチェック弁４１は、環状
油路３５すなわち油圧発生室４０に常時連通しながらダ
ンパ室３９に臨んで開口して弁駆動ピストン１３に穿設
される弁孔４２と、該弁孔４２をダンパ室３９側から閉
塞可能な球状の弁体４３と、該弁体４３を開閉動可能に
保持すべく弁駆動ピストン１３に固定される帽状リテー
ナ４４とを備える。弁孔４２のダンパ室３９への開口端
には弁体４３を着座可能な弁座４５が弁体４３に対応し
て半球状に形成される。またリテーナ４４には該リテー
ナ４４内とダンパ室３９とを連通する複数の連通孔４６
が設けられる。The valve driving piston 13 has a hydraulic pressure generating chamber 40.
A check valve 41 is provided that only allows flow of hydraulic oil from the damper chamber 39 to the damper chamber 39. This check valve 41 has a valve hole 42 that opens facing the damper chamber 39 and is bored in the valve driving piston 13 while always communicating with the annular oil passage 35, that is, the oil pressure generation chamber 40, and a valve hole 42 that is opened in the damper chamber 39 and is connected to the damper chamber. The valve body 43 includes a spherical valve body 43 that can be closed from the 39 side, and a cap-shaped retainer 44 that is fixed to the valve driving piston 13 to hold the valve body 43 so that it can be opened and closed. At the opening end of the valve hole 42 to the damper chamber 39, a valve seat 45 on which a valve body 43 can be seated is formed in a hemispherical shape corresponding to the valve body 43. Further, the retainer 44 has a plurality of communication holes 46 that communicate the inside of the retainer 44 and the damper chamber 39.
will be provided.
【００１６】かかるチェック弁４１では、ダンパ室３９
すわちリテーナ４４内の油圧により弁体４３を下方に押
下げる力が弁孔４２内の油圧により弁体４３を上方に押
上げる力を上回ったときに弁体４３が弁座４５に着座し
て閉弁する。In this check valve 41, the damper chamber 39
That is, when the force pushing down the valve body 43 due to the hydraulic pressure in the retainer 44 exceeds the force pushing the valve body 43 upward due to the hydraulic pressure in the valve hole 42, the valve body 43 is seated on the valve seat 45. Close the valve.
【００１７】カム従動ピストン１５は、閉塞端を下方に
した有底円筒状に形成されており、このカム従動ピスト
ン１５の上部開口端はリフタ１４に当接し得る閉塞部材
４７で閉塞される。またリフタ１４は、その閉塞端外面
をカム９に摺接させるようにして有底円筒状に形成され
ており、第１孔部１８に摺動可能に嵌合される。しかも
リフタ１４の閉塞端内面中央部には、前記カム従動ピス
トン１５の閉塞部材４７に当接する当接突起１４ａが突
設される。The cam driven piston 15 is formed into a bottomed cylindrical shape with the closed end facing downward, and the upper open end of the cam driven piston 15 is closed by a closing member 47 that can come into contact with the lifter 14. Further, the lifter 14 is formed into a bottomed cylindrical shape so that the outer surface of the closed end is in sliding contact with the cam 9, and is slidably fitted into the first hole 18. Furthermore, an abutting protrusion 14 a that abuts against the closing member 47 of the cam driven piston 15 is protrudingly provided at the center of the inner surface of the closed end of the lifter 14 .
【００１８】カム従動ピストン１５と閉塞部材５４との
間には、貯留室４８が形成されており、閉塞部材４７に
は、貯留室４８に貯留された作動油をカム９との摺接部
に導く透孔４９が穿設される。またカム従動ピストン１
５の下部閉塞端には油圧発生室４０に通じ得る油孔５０
が穿設され、該油孔５０には、貯留室４８から油圧発生
室４０側への作動油の流のみを許容するチェック弁５１
が配設される。A storage chamber 48 is formed between the cam driven piston 15 and the closing member 54, and the closing member 47 supplies the hydraulic oil stored in the storage chamber 48 to the sliding portion with the cam 9. A guiding through hole 49 is bored. Also, cam driven piston 1
5 has an oil hole 50 at the lower closed end that can communicate with the oil pressure generation chamber 40.
A check valve 51 is provided in the oil hole 50 to allow the flow of hydraulic oil only from the storage chamber 48 to the oil pressure generation chamber 40 side.
will be placed.
【００１９】油圧発生手段１０の油圧発生室４０とダン
パ室３９との間には、弁駆動ピストン１３の閉弁方向作
動時（上昇作動時）に下部シリンダ孔３３の途中に設定
される油圧緩衝開始位置Ｐとしての環状凹部３６の後縁
を弁駆動ピストン１３の後端（上端）が通過したときか
ら油圧発生室４０への作動油の戻り量を徐々に絞るべく
開口面積を可変とした可変オリフィス５３と、下部シリ
ンダ孔３３内での弁駆動ピストン１３の移動にかかわら
ず開口面積が一定である固定オリフィス５７とが介設さ
れる。A hydraulic buffer is provided between the hydraulic pressure generating chamber 40 of the hydraulic pressure generating means 10 and the damper chamber 39, which is set in the middle of the lower cylinder hole 33 when the valve drive piston 13 is operated in the valve closing direction (during upward operation). The opening area is variable in order to gradually reduce the amount of hydraulic oil returning to the hydraulic pressure generation chamber 40 from the time when the rear end (upper end) of the valve drive piston 13 passes the rear edge of the annular recess 36 serving as the starting position P. An orifice 53 and a fixed orifice 57 whose opening area remains constant regardless of the movement of the valve drive piston 13 within the lower cylinder hole 33 are provided.
【００２０】図３を併せて参照して、弁駆動ピストン１
３の後縁部すなわち上端部には薄肉部１３ａが設けられ
ており、この薄肉部１３ａには、シリンダ体１２におけ
る環状凹部３６と共働して可変オリフィス５３を構成す
る切欠き部５５が設けられる。しかも可変オリフィス５
３は、吸気弁５の着座直前に開口面積が０となるように
、すなわち吸気弁５が着座したときには環状凹部３６の
上端縁が切欠き部５５よりも下方位置となるように設定
される。Referring also to FIG. 3, the valve drive piston 1
A thin wall portion 13a is provided at the rear edge or upper end of the cylinder body 3, and a cutout portion 55 that cooperates with the annular recess 36 in the cylinder body 12 to form a variable orifice 53 is provided in the thin wall portion 13a. It will be done. Moreover, variable orifice 5
3 is set so that the opening area becomes 0 immediately before the intake valve 5 is seated, that is, the upper edge of the annular recess 36 is positioned below the notch 55 when the intake valve 5 is seated.
【００２１】一方、固定オリフィス５７は、ダンパ室３
９の上端に連通すべく、油圧発生手段１０の油圧発生室
４０およびダンパ室３９を隔てる仕切壁３２の中央部に
穿設される。On the other hand, the fixed orifice 57 is located in the damper chamber 3.
9 is bored in the center of the partition wall 32 that separates the hydraulic pressure generating chamber 40 and the damper chamber 39 of the hydraulic pressure generating means 10 .
【００２２】このような可変オリフィス５３および固定
オリフィス５７によると、図４の実線で示すように、吸
気弁５の閉弁時に点Ａから範囲Ｂで示す部分ではダンパ
室３９の作動油が可変オリフィス５３および固定オリフ
ィス５７により制限されながらリークし、その作動油リ
ークに応じて吸気弁５が閉弁作動するが、吸気弁５の着
座直前であるＣ点では可変オリフィス５３の開口面積は
０となり、その後の範囲Ｄで示す部分では固定オリフィ
ス５７の絞り作用のみにより作動油のリーク量が制限さ
れるので、範囲Ｄでは弁リフトの傾きがＣ点での傾きの
ままとなる。According to the variable orifice 53 and the fixed orifice 57, as shown by the solid line in FIG. 53 and the fixed orifice 57, and the intake valve 5 closes in response to the hydraulic oil leak, but at point C, which is just before the intake valve 5 is seated, the opening area of the variable orifice 53 becomes 0, In the subsequent region D, the amount of hydraulic oil leaked is limited only by the throttling action of the fixed orifice 57, so in the region D, the slope of the valve lift remains the same as at point C.
【００２３】次にこの実施例の作用について説明すると
、吸気弁５の全閉状態では、油圧発生手段１０は図２で
示す状態にあり、この図２の状態からカムシャフト８の
回転に応じてカム９によりリフタ１４が押下げられる。
それによりカム従動ピストン１５が下方に押圧駆動され
、油圧発生室４０の容積が収縮せしめられ、油圧発生室
４０内の作動油は油路３７を経て環状油路３５に導かれ
、さらに固定オリフィス５４を経てダンパ室３９に導入
される。このとき、チェック弁４１の弁体４３には、ダ
ンパ室３９の油圧による下向の力と、弁孔４２に導入さ
れた油圧による上向きの力とが作用しており、前記上向
きの力が下向きの力よりも大きくなったときに弁体４３
が弁座４５から離反し、作動油がダンパ室３９に導入さ
れる。したがってダンパ室３９の油圧が大となり、弁駆
動ピスン１３が下方に押下げられる。この弁駆動ピスト
ン１３の下方への摺動途中で環状油路３５はダンパ室３
９に直接連通し、ダンパ室３９への油の流入量がさらに
大となり、弁駆動ピストン１３はさらに押下げられる。
これにより吸気弁５が弁ばね７のばね力に抗して開弁駆
動される。Next, the operation of this embodiment will be explained. When the intake valve 5 is fully closed, the hydraulic pressure generating means 10 is in the state shown in FIG. 2, and from this state shown in FIG. The lifter 14 is pushed down by the cam 9. As a result, the cam driven piston 15 is pushed downward, the volume of the oil pressure generation chamber 40 is contracted, and the hydraulic oil in the oil pressure generation chamber 40 is guided to the annular oil passage 35 via the oil passage 37, and further to the fixed orifice 54. It is introduced into the damper chamber 39 through the. At this time, a downward force due to the hydraulic pressure in the damper chamber 39 and an upward force due to the hydraulic pressure introduced into the valve hole 42 are acting on the valve body 43 of the check valve 41, and the upward force is applied downwardly. When the force becomes larger than the force of the valve body 43
is separated from the valve seat 45, and hydraulic oil is introduced into the damper chamber 39. Therefore, the oil pressure in the damper chamber 39 increases, and the valve drive piston 13 is pushed downward. During the downward sliding of the valve drive piston 13, the annular oil passage 35 connects to the damper chamber 3.
9, the amount of oil flowing into the damper chamber 39 becomes even larger, and the valve driving piston 13 is further pushed down. As a result, the intake valve 5 is driven to open against the spring force of the valve spring 7.
【００２４】吸気弁５が全開状態になった後に、カム９
によるリフタ１４への押圧力が解除されると、吸気弁５
は弁ばね７のばね力により上方すなわち閉弁方向に駆動
される。この吸気弁５の閉弁作動により弁駆動ピストン
１３も上方に押上げられ、ダンパ室３９の作動油は環状
油路３５および油路３７を経て油圧発生室４０に戻され
るが、その閉弁作途中で環状凹部３６およびダンパ室３
９間の直接の連通状態が解除され、ダンパ室３９および
環状油路３５すなわち油圧発生室４０間にチェック弁４
１と、可変オリフィス５３および固定オリフィス５７と
が介在するようになってからは、ダンパ室３９から油圧
発生室４０への作動油の戻り量が制限される。すなわち
チェック弁４１では、弁体４３にかかる下向きの力が上
向きの力よりも大きくなり、弁体４３は弁座４５に着座
するので、ダンパ室３９および油圧発生室４０間は可変
オリフィス５３および固定オリフィス５７を介して連通
することになり、これらのオリフィス５３，５７による
絞り作用によりダンパ室３９から油圧発生室４０への作
動油の戻り量が制限される。このため、吸気弁５の上方
への移動速度すなわち閉弁速度が閉弁作動途中から緩め
られ、吸気弁５は弁座部材４に緩やかに着座することに
なる。したがって着座時の衝撃が緩和され、吸気弁５お
よび弁座部材４等の損傷を極力防止することができる。After the intake valve 5 is fully open, the cam 9
When the pressing force on the lifter 14 is released, the intake valve 5
is driven upward, that is, in the valve closing direction, by the spring force of the valve spring 7. This valve closing operation of the intake valve 5 also pushes the valve drive piston 13 upward, and the hydraulic oil in the damper chamber 39 is returned to the oil pressure generation chamber 40 via the annular oil passage 35 and the oil passage 37. An annular recess 36 and a damper chamber 3 are formed in the middle.
The direct communication state between the damper chamber 39 and the annular oil passage 35, that is, the hydraulic pressure generation chamber 40 is released, and the check valve 4
1, the variable orifice 53, and the fixed orifice 57, the amount of hydraulic fluid that returns from the damper chamber 39 to the hydraulic pressure generating chamber 40 is limited. That is, in the check valve 41, the downward force applied to the valve body 43 is greater than the upward force, and the valve body 43 is seated on the valve seat 45, so that the variable orifice 53 and the fixed The two orifices 53 and 57 communicate with each other through the orifice 57, and the amount of hydraulic oil that returns from the damper chamber 39 to the hydraulic pressure generation chamber 40 is limited by the throttling action of these orifices 53 and 57. Therefore, the upward movement speed of the intake valve 5, that is, the valve closing speed, is slowed midway through the valve closing operation, and the intake valve 5 is seated gently on the valve seat member 4. Therefore, the impact upon seating is alleviated, and damage to the intake valve 5, valve seat member 4, etc. can be prevented as much as possible.
【００２５】しかも固定オリフィス５７は、下部シリン
ダ孔３３の上端に連通して仕切壁３２に穿設されるもの
であり、ダンパ室３９の上端は該固定オリフィス５７を
介して油圧発生室４０に連通している。したがって作動
油中に混入したエアーがダンパ室３９内に入ってきても
、固定オリフィス５７を介してその空気を油圧発生室４
０側に逃がすことができる。したがってダンパ室３９内
にエアーが侵入することによるダンパ室３９の剛性低化
を回避することができ、その結果、弁リフト量の不足や
バルブジャンプが生じることを防止して吸気弁５の円滑
な作動を確保することができる。Moreover, the fixed orifice 57 is bored in the partition wall 32 so as to communicate with the upper end of the lower cylinder hole 33, and the upper end of the damper chamber 39 communicates with the hydraulic pressure generation chamber 40 through the fixed orifice 57. are doing. Therefore, even if air mixed in the hydraulic oil enters the damper chamber 39, the air is transferred to the hydraulic pressure generating chamber 39 through the fixed orifice 57.
It can be released to the 0 side. Therefore, it is possible to avoid a decrease in the rigidity of the damper chamber 39 due to air entering the damper chamber 39, and as a result, it is possible to prevent the insufficient valve lift amount and valve jump from occurring, and to maintain the smooth operation of the intake valve 5. Operation can be ensured.
【００２６】上記実施例では、固定オリフィス５７を仕
切壁３２に設けたが、ダンパ室３９の上端に連通するよ
うにしてシリンダ体１２の側壁に固定オリフィスを設け
るようにしてもよい。In the above embodiment, the fixed orifice 57 is provided in the partition wall 32, but the fixed orifice 57 may be provided in the side wall of the cylinder body 12 so as to communicate with the upper end of the damper chamber 39.
【００２７】また上記実施例では、吸気弁５の動弁装置
について説明したが、本発明は、排気弁の動弁装置につ
いても同様に実施可能である。さらに油圧発生手段とし
ては、上記各実施例のようにカムにより油圧を発生する
ものだけでなく、油圧ポンプ等の油圧発生源からの油圧
を制御弁で制御してダンパ室に供給するようにしたもの
であってもよい。Further, in the above embodiment, a valve operating system for the intake valve 5 has been described, but the present invention can be similarly implemented for a valve operating system for an exhaust valve. Furthermore, the hydraulic pressure generating means is not limited to one that generates hydraulic pressure using a cam as in each of the above embodiments, but the hydraulic pressure from a hydraulic pressure generating source such as a hydraulic pump is controlled by a control valve and supplied to the damper chamber. It may be something.
【００２８】[0028]
【発明の効果】以上のように本発明によれば、固定オリ
フィスは、ダンパ室の上端に連通してシリンダ体に設け
られるので、ダンパ室内に侵入したエアーを固定オリフ
ィスから油圧発生手段側に逃がすことができ、機関弁の
円滑な作動を確実に得ることができる。[Effects of the Invention] As described above, according to the present invention, the fixed orifice is provided in the cylinder body so as to communicate with the upper end of the damper chamber, so that air that has entered the damper chamber is released from the fixed orifice to the hydraulic pressure generating means side. This ensures smooth operation of the engine valve.
【図１】全体縦断側面図である。FIG. 1 is an overall longitudinal sectional side view.
【図２】図１の要部拡大縦断面図である。FIG. 2 is an enlarged vertical cross-sectional view of the main part of FIG. 1;
【図３】弁駆動ピストンの拡大斜視図である。FIG. 3 is an enlarged perspective view of the valve drive piston.
【図４】弁リフト特性線図である。FIG. 4 is a valve lift characteristic diagram.
５ 機関弁としての吸気弁 １０ 油圧発生手段 １２ シリンダ体 １３ 弁駆動ピストン ３３ シリンダ孔 ３７ 油路 ３９ ダンパ室 ４１ チェック弁 ５７ 固定オリフィス 5 Intake valve as engine valve 10 Hydraulic pressure generation means 12 Cylinder body 13 Valve driven piston 33 Cylinder hole 37 Oil road 39 Damper room 41 Check valve 57 Fixed orifice
Claims (1)
固定のシリンダ体（１２）に設けられ、該シリンダ孔（
３３）には、閉弁方向にばね付勢された機関弁（５）に
下端部が連動、連結されるとともにシリンダ孔（３３）
の上部閉塞端との間にダンパ室（３９）を形成する弁駆
動ピストン（１３）が摺動可能に嵌合され、機関弁（５
）の開弁時期に対応して油圧を発生する油圧発生手段（
１０）と前記ダンパ室（３９）との間には、前記油圧発
生手段（１０）からダンパ室（３９）への作動油の流通
のみを許容するチェック弁（４１）と、固定オリフィス
（５７）とが介設され、シリンダ体（１２）には、弁駆
動ピストン（１３）が機関弁（５）の全閉状態から所定
距離以上開弁方向に移動したときにダンパ室（３９）に
連通すべくシリンダ孔（３３）の内面に開口する油路（
３７）が油圧発生手段（１０）に常時連通して設けられ
る内燃機関用機関弁の油圧駆動装置において、固定オリ
フィス（５７）は、ダンパ室（３９）の上端に連通して
シリンダ体（１２）に設けられることを特徴とする内燃
機関用機関弁の油圧駆動装置。Claim 1: A cylinder hole (33) whose upper end is closed is provided in a fixed cylinder body (12), and the cylinder hole (33) is provided in a fixed cylinder body (12).
33), the lower end of which is interlocked and connected to the engine valve (5) which is spring-biased in the valve closing direction, and the cylinder hole (33)
A valve driving piston (13) forming a damper chamber (39) between the upper closed end of the engine valve (5) and the engine valve (5) is slidably fitted.
Hydraulic pressure generating means (
10) and the damper chamber (39), there is a check valve (41) that allows only the flow of hydraulic oil from the hydraulic pressure generating means (10) to the damper chamber (39), and a fixed orifice (57). The cylinder body (12) is provided with a damper chamber (39) that communicates with the damper chamber (39) when the valve driving piston (13) moves from the fully closed state of the engine valve (5) in the valve opening direction for a predetermined distance or more. An oil passage (
In the hydraulic drive device for an engine valve for an internal combustion engine, the fixed orifice (57) communicates with the upper end of the damper chamber (39) and is connected to the cylinder body (12). A hydraulic drive device for an engine valve for an internal combustion engine, characterized in that it is provided in a.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3028692A JPH04214915A (en) | 1991-02-22 | 1991-02-22 | Hydraulic driving device of engine valve for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3028692A JPH04214915A (en) | 1991-02-22 | 1991-02-22 | Hydraulic driving device of engine valve for internal combustion engine |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1188531A Division JPH0354308A (en) | 1989-07-20 | 1989-07-20 | Hydraulic driving device of engine valve for internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH04214915A true JPH04214915A (en) | 1992-08-05 |
Family
ID=12255538
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3028692A Pending JPH04214915A (en) | 1991-02-22 | 1991-02-22 | Hydraulic driving device of engine valve for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH04214915A (en) |
-
1991
- 1991-02-22 JP JP3028692A patent/JPH04214915A/en active Pending
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