JP3023803B2 - Oil supply device for internal combustion engine - Google Patents
Oil supply device for internal combustion engineInfo
- Publication number
- JP3023803B2 JP3023803B2 JP2408255A JP40825590A JP3023803B2 JP 3023803 B2 JP3023803 B2 JP 3023803B2 JP 2408255 A JP2408255 A JP 2408255A JP 40825590 A JP40825590 A JP 40825590A JP 3023803 B2 JP3023803 B2 JP 3023803B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- valve
- hydraulic
- engine
- passage
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/12—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/12—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10
- F01M2001/123—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10 using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
- F01M9/10—Lubrication of valve gear or auxiliaries
- F01M9/108—Lubrication of valve gear or auxiliaries of auxiliaries
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M1/00—Carburettors with means for facilitating engine's starting or its idling below operational temperatures
- F02M1/02—Carburettors with means for facilitating engine's starting or its idling below operational temperatures the means to facilitate starting or idling being chokes for enriching fuel-air mixture
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
- Valve Device For Special Equipments (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、シリンダヘッドに開閉
作動可能に支持された機関弁およびクランク軸間に、油
圧室の油圧変化に応じて前記機関弁の作動特性を変更可
能な弁作動特性変更手段が介設されて成る動弁装置を備
えた内燃機関における給油装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve operating characteristic between an engine valve and a crankshaft supported on a cylinder head so as to be capable of opening and closing, the operating characteristic of the engine valve being changeable in response to a change in oil pressure in a hydraulic chamber. The present invention relates to a refueling device in an internal combustion engine provided with a valve train in which a change means is provided.
【０００２】[0002]
【従来の技術】従来、かかる動弁装置を備えた内燃機関
は、たとえば特開昭６１−２２９９１２号公報および特
開昭６１−２７５５１６号公報等により既に知られてお
り、これらの内燃機関において、弁作動特性変更手段の
油圧室に作動油を供給するためのオイルポンプは、機関
本体のオイルパンから作動油を汲上げるようにしてい
る。しかるに、オイルポンプは機関本体の下部に設置さ
れるのが一般的であるので、シリンダヘッドすなわち機
関本体の上部に配設される弁作動特性変更手段の油圧室
とオイルポンプとの間の距離が比較的長く、したがって
機関始動時の油圧室への給油が遅れがちとなる。2. Description of the Related Art Conventionally, an internal combustion engine equipped with such a valve train is already known, for example, from JP-A-61-229912 and JP-A-61-275516. An oil pump for supplying hydraulic oil to the hydraulic chamber of the valve operating characteristic changing means draws hydraulic oil from an oil pan of the engine body. However, since the oil pump is generally installed at the lower part of the engine body, the distance between the oil pump and the hydraulic chamber of the cylinder head, that is, the valve operating characteristic changing means provided at the upper part of the engine body, is reduced. Relatively long, so that the oil supply to the hydraulic chamber when the engine is started tends to be delayed.
【０００３】そこで、本出願人は、弁作動特性変更手段
の油圧室および動弁系の各潤滑部に接続されるヘッド専
用オイルポンプをシリンダヘッドに配設し、このヘッド
専用オイルポンプによりシリンダヘッドに設けられたオ
イルバスから作動油を汲上げるようにした給油装置を既
に提案（特願平２−４７０５６号）している。Accordingly, the present applicant has arranged on a cylinder head a dedicated oil pump for head connected to a hydraulic chamber of a valve operating characteristic changing means and each lubricating portion of a valve operating system. (Japanese Patent Application No. 2-47056) has already proposed a lubricating apparatus for pumping hydraulic oil from an oil bath provided in the company.
【０００４】[0004]
【発明が解決しようとする課題】ところが、上記提案技
術では、機関本体下部のオイルパンから油を汲上げるオ
イルポンプを機関本体下部の各作動油消費部に接続して
成る給油系と、オイルバスから油を汲上げるヘッド専用
オイルポンプを弁作動特性変更手段の油圧室および動弁
系の各潤滑部に接続して成る給油系とが相互に独立して
設けられており、オイルパンおよびオイルバスは相互に
連通していないので、オイル交換および補給等のメンテ
ナンスを両給油系でそれぞれ独立して行なわねばなら
ず、メンテナンス作業が面倒である。またヘッド専用オ
イルポンプは、機関のクランク軸に連動、連結されるも
のであって機関の回転数増大に応じて吐出量が大となる
ものである。而して弁作動特性変更手段は、たとえば油
圧室の油圧で弁駆動ピストンを押圧駆動するとともに油
圧室の油圧解放時期を制御することより機関弁の作動都
政を変更するようにしたタイプのものにあっては、機関
始動時およびアイドル時等の機関低速回転時に比較的大
量の油が必要であって機関高速回転時にはそれ程多くの
油を必要としないのに対し、動弁系の各潤滑部では機関
の回転数が大となるにつれて多くの油を必要とするもの
である。このように機関回転数に対する必要油量特性が
異なる部位にヘッド専用オイルポンプから油を供給する
ようにしていると、機関の低速回転時に必要な油量に基
づいてヘッド専用オイルポンプの容量を決定せざるを得
ないことから機関高速回転時にはヘッド専用オイルポン
プの容量が過大となり、フリクションロスが大きくな
る。However, in the above-mentioned proposed technique, an oil supply system in which an oil pump for pumping oil from an oil pan at a lower portion of the engine body is connected to each hydraulic oil consuming portion at a lower portion of the engine body, and an oil bath. An oil pump formed by connecting a head dedicated oil pump for pumping oil from the hydraulic chamber of the valve operating characteristic changing means and each lubricating portion of the valve operating system is provided independently of each other, and an oil pan and an oil bath are provided. Are not communicated with each other, maintenance such as oil change and replenishment must be performed independently in both oil supply systems, and maintenance work is troublesome. The head-only oil pump is linked to and connected to the crankshaft of the engine, and has a large discharge amount as the engine speed increases. Thus, the valve operating characteristic changing means is, for example, of a type in which the valve operating piston is pressed and driven by the hydraulic pressure of the hydraulic chamber and the timing of releasing the hydraulic pressure of the hydraulic chamber is controlled to change the operating condition of the engine valve. Therefore, a relatively large amount of oil is required at the time of engine start and idling and at low engine speeds, and not so much oil is needed at high engine speeds. As the engine speed increases, more oil is required. As described above, when the oil dedicated to the head is supplied from the head dedicated oil pump to the portions having different required oil amount characteristics with respect to the engine speed, the capacity of the dedicated head oil pump is determined based on the required oil amount at the time of low speed rotation of the engine. Since the engine must be driven, the capacity of the head dedicated oil pump becomes excessive when the engine rotates at high speed, and the friction loss increases.
【０００５】本発明は、かかる事情に鑑みてなされたも
のであり、オイル交換および補給等のメンテナンスを容
易とし、しかも機関高速回転時のフリクションロス低減
を可能とした内燃機関における給油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 an oil supply device for an internal combustion engine that facilitates maintenance such as oil replacement and replenishment, and that can reduce friction loss during high-speed rotation of the engine. The purpose is to:
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するため
に請求項１の発明によれば、機関本体の下部に設けられ
たオイルパンから作動油を汲み上げる第１オイルポンプ
には作動油消費部に通じる給油路が接続され、クランク
軸に連なる動弁カム軸を含む動弁系の各潤滑部に通じる
動弁系潤滑用分岐油路が前記給油路から分岐され、シリ
ンダヘッドには、前記動弁系の各潤滑部から漏出した油
を受容可能であるとともに前記オイルパンに余剰油を溢
流可能なオイルバスが設けられ、該オイルバスから作動
油を汲上げる第２オイルポンプが前記弁作動特性変更手
段の油圧室に接続され、動弁系潤滑用分岐油路には、オ
イルバスに直接通じる通路が接続される。 According to the first aspect of the present invention , there is provided a first oil pump for pumping hydraulic oil from an oil pan provided at a lower portion of an engine body. A lubricating passage is connected to the lubricating passage, and a branching lubricating passage for lubricating the valve system, which communicates with each lubricating portion of the valve operating system including the valve operating camshaft connected to the crankshaft, is branched from the lubricating passage. An oil bath capable of receiving the oil leaked from each lubricating portion of the valve system and allowing the excess oil to overflow into the oil pan is provided, and a second oil pump for pumping hydraulic oil from the oil bath is provided with the valve operating valve. It is connected to the hydraulic chamber of the characteristic changing means , and
A passage leading directly to Irbus is connected.
【０００７】[0007]
【０００８】また請求項２の発明によれば、機関本体の
下部に設けられたオイルパンから作動油を汲み上げる第
１オイルポンプには作動油消費部に通じる給油路が接続
され、クランク軸に連なる動弁カム軸を含む動弁系の各
潤滑部に通じる動弁系潤滑用分岐油路が前記給油路から
分岐され、シリンダヘッドには、前記動弁系の各潤滑部
から漏出した油を受容可能であるとともに前記オイルパ
ンに余剰油を溢流可能なオイルバスが設けられ、該オイ
ルバスから作動油を汲上げる第２オイルポンプが前記弁
作動特性変更手段の油圧室に接続され、シリンダヘッド
に結着されるヘッドカバーに設けられる給油口あるいは
該給油口に通じる導入口が、前記オイルバスの直上に配
設される。According to the second aspect of the present invention , the engine body
Pumping hydraulic oil from the oil pan provided at the bottom
1 Oil pump is connected to oil supply passage leading to hydraulic oil consumption section
Of the valve train including the valve train camshaft connected to the crankshaft.
A branch oil passage for valve system lubrication leading to the lubrication section
The cylinder head is divided into lubricating parts of the valve train.
Oil that leaks from the
An oil bath that allows excess oil to overflow is provided in the oil
The second oil pump that pumps hydraulic oil from the
An oil supply port connected to the hydraulic chamber of the operating characteristic changing means and provided in a head cover connected to the cylinder head or an introduction port communicating with the oil supply port is disposed immediately above the oil bath.
【０００９】[0009]
【実施例】以下、図面により本発明の実施例について説
明すると、図１ないし図５は本発明の一実施例を示すも
のであり、図１は内燃機関の給油系統図、図２は弁作動
特性変更手段の構成を示す縦断面図、図３は図２の３−
３線に沿うシリンダヘッドの断面図、図４は機関弁の作
動特性図、図５は機関負荷に対する弁作動特性変更手段
の必要油量特性図である。1 to 5 show an embodiment of the present invention. FIG. 1 is a diagram of a refueling system of an internal combustion engine, and FIG. 2 is a valve operation. FIG. 3 is a vertical sectional view showing the configuration of the characteristic changing means, and FIG.
FIG. 4 is a sectional view of the cylinder head taken along the line 3, FIG. 4 is an operating characteristic diagram of the engine valve, and FIG.
【００１０】先ず図１において、機関本体Ｅには、潤滑
用給油系ＯL と弁作動特性変更手段用給油系ＯV とが配
設される。而して潤滑用給油系Ｏ L は、機関本体Ｅの下
部に配設されているオイルパン１から作動油を汲上げる
第１オイルポンプＰの吐出口に、フィルタ４を備える給
油路５がリリーフ弁２を介して接続され、給油路５から
分岐した分岐油路６が機関本体Ｅの下部に配設されてい
るクランクジャーナル部８およびクーリングジェット９
・・・等の作動油消費部にそれぞれ接続されるととも
に、機関本体Ｅの上部を構成するシリンダヘッド１１に
配設された動弁系における複数の潤滑部すなわちカムジ
ャーナル部１２およびカムシャワー部１３・・・等に通
じる動弁系潤滑用分岐油路７が給油路５から分岐されて
成る。しかも動弁系潤滑用分岐油路７の途中にはオリフ
ィス１０が介設されている。[0010] First, in FIG. 1, the engine body E, and a lubricating oil supply system O L refueling system for a valve operating characteristic changing means O V is disposed. Thus the lubricating oil supply system O L and the working oil from the oil pan 1 is disposed in the lower portion of the engine body E to the discharge port of the pumping gel first oil pump P, the oil supply passage 5 comprises a filter 4 relief A branch oil passage 6, which is connected through the valve 2 and branches from the oil supply passage 5, is provided at a lower portion of the engine body E with a crank journal portion 8 and a cooling jet 9.
, Etc., and a plurality of lubricating portions, ie, a cam journal portion 12 and a cam shower portion 13 in a valve train provided in a cylinder head 11 constituting an upper portion of the engine body E. , Etc., are branched from the oil supply passage 5. In addition, an orifice 10 is provided in the middle of the valve system lubrication branch oil passage 7.
【００１１】シリンダヘッド１１には、動弁系における
複数の潤滑部すなわちカムジャーナル部１２およびカム
シャワー部１３・・・等から漏出した油を受けるべくオ
イルバス１４が設けられており、該オイルバス１４に直
接連通する通路１５が前記動弁系潤滑用分岐油路７に接
続され、該通路１５にはオリフィス１６が介設される。
したがってオイルバス１４には、機関作動中にはオイル
ポンプＰから吐出される油の一部がオリフィス１０，１
６で絞られて常時供給されることになる。The cylinder head 11 is provided with an oil bath 14 for receiving oil leaked from a plurality of lubricating portions in the valve train, that is, the cam journal portion 12 and the cam shower portions 13... A passage 15 directly communicating with 14 is connected to the valve system lubrication branch oil passage 7, and an orifice 16 is interposed in the passage 15.
Therefore, a part of the oil discharged from the oil pump P during the operation of the engine is supplied to the orifice 10, 1.
It is squeezed at 6 and always supplied.
【００１２】弁作動特性変更手段用給油系ＯV は、シリ
ンダヘッド１１に設けられているオイルバス１４から作
動油を汲上げるべく前記シリンダヘッド１１に配設され
た第２オイルポンプＰC の吐出口に、フィルタ１７およ
び調圧弁１８を備える専用給油路１９がリリーフ弁２０
を介して接続され、該専用給油路１９が弁作動特性変更
手段２１に接続されて成る。[0012] valve operating characteristic changing means for refueling system O V is ejection of the second oil pump P C disposed in the cylinder head 11 Beku pumping gels hydraulic oil from the oil bath 14 provided in the cylinder head 11 At the outlet, a dedicated oil supply passage 19 having a filter 17 and a pressure regulating valve 18 is provided with a relief valve 20.
, And the exclusive oil supply passage 19 is connected to the valve operating characteristic changing means 21.
【００１３】弁作動特性変更手段２１は、機関弁の作動
特性を機関の運転状態に応じて変更可能なものであり、
次に図２および図３を参照しながら弁作動特性変更手段
２１に関連する部分の構成について説明する。The valve operating characteristic changing means 21 can change the operating characteristics of the engine valve according to the operating state of the engine.
Next, the configuration of a portion related to the valve operating characteristic changing means 21 will be described with reference to FIGS.
【００１４】シリンダヘッド１１には、図示しないシリ
ンダブロックとの間に形成される燃焼室２２の頂部に開
口する吸気弁口２３が吸気ポート２４に通じて穿設され
るとともに、吸気弁口２３を開閉可能な機関弁としての
吸気弁Ｖが上下移動自在に配設される。該吸気弁Ｖの上
端部には鍔部２５が設けられ、該鍔部２５とシリンダヘ
ッド１１との間には弁ばね２６が縮設される。而して吸
気弁Ｖは、弁ばね２６のばね力により上方すなわち閉弁
方向に向けて付勢される。The cylinder head 11 is provided with an intake valve port 23 which is opened at the top of a combustion chamber 22 formed between the cylinder head 11 and a cylinder block (not shown) through an intake port 24. An intake valve V as an openable and closable engine valve is disposed to be vertically movable. A flange 25 is provided at an upper end of the intake valve V, and a valve spring 26 is contracted between the flange 25 and the cylinder head 11. Thus, the intake valve V is urged upward, that is, in the valve closing direction by the spring force of the valve spring 26.
【００１５】一方、シリンダヘッド１１の上部には、動
弁カム軸２７が回転自在に配設されており、この動弁カ
ム軸２７の一端に設けられたプーリ３３に図示しない無
端ベルトを介してクランク軸からの動力が伝達される。
また第２オイルポンプＰC は、動弁カム軸２７の他端に
連結されてシリンダヘッド１１に付設される。動弁カム
軸２７には、各気筒の吸気弁Ｖに対応する吸気側動弁カ
ム２８と、各気筒の排気弁（図示せず）に対応する排気
側動弁カム２９とが一体に設けられており、各吸気側動
弁カム２８の回転作動が弁作動特性変更手段２１を介し
て各吸気弁Ｖに伝達され、各排気側動弁カム２９の回転
作動は該カム２９に摺接するロッカアーム３０を介して
各排気弁に伝達される。On the other hand, a valve operating cam shaft 27 is rotatably disposed above the cylinder head 11, and a pulley 33 provided at one end of the valve operating cam shaft 27 is connected to a pulley 33 via an endless belt (not shown). Power from the crankshaft is transmitted.
The second oil pump P C is coupled to the other end of the valve operating cam shaft 27 is attached to the cylinder head 11. The valve cam shaft 27 is integrally provided with an intake valve cam 28 corresponding to the intake valve V of each cylinder and an exhaust valve cam 29 corresponding to an exhaust valve (not shown) of each cylinder. The rotation operation of each intake valve cam 28 is transmitted to each intake valve V via the valve operation characteristic changing means 21, and the rotation operation of each exhaust valve cam 29 is slidably contacted with the rocker arm 30. To each exhaust valve.
【００１６】弁作動特性変更手段２１は、吸気弁Ｖおよ
び吸気側動弁カム２８間に介設される伝動機構３１と、
該伝動機構３１における油圧室４１に接続される油圧回
路３２とを備える。The valve operating characteristic changing means 21 includes: a transmission mechanism 31 interposed between the intake valve V and the intake valve cam 28;
A hydraulic circuit 32 connected to a hydraulic chamber 41 in the transmission mechanism 31.
【００１７】伝動機構３１は、シリンダヘッド１１の上
部に固定された支持ブロック３４に吸気弁Ｖと同軸にし
て固定される第１シリンダ体３５と、吸気弁Ｖの上端に
当接するとともに第１シリンダ体３５との間にダンパ室
３６を画成して第１シリンダ体３５の下部に摺動可能に
嵌合される弁駆動ピストン３７と、吸気側動弁カム２８
の上方で支持ブロック３４に固定される第２シリンダ体
３８と、吸気側動弁カム２８に摺接しながら支持ブロッ
ク３４に摺動可能に嵌合されるリフタ３９と、該リフタ
３９に上端を当接させるとともに第２シリンダ体３８と
の間に油圧室４１を画成して第２シリンダ体３８の下部
に摺動可能に嵌合されるカム従動ピストン４０とを備え
る。The transmission mechanism 31 includes a first cylinder body 35 fixed to a support block 34 fixed to the upper portion of the cylinder head 11 coaxially with the intake valve V; A valve driving piston 37 slidably fitted to a lower portion of the first cylinder body 35 by defining a damper chamber 36 between the valve driving piston 37 and the intake side valve actuating cam 28.
A lifter 39 slidably fitted to the support block 34 while slidingly contacting the intake side valve operating cam 28, and an upper end of the lifter 39. A cam driven piston 40 is provided which is in contact with the second cylinder body 38, defines a hydraulic chamber 41 between the second cylinder body 38, and is slidably fitted to a lower portion of the second cylinder body 38.
【００１８】第１シリンダ体３５の内面には前記油圧室
４１に常時連通する環状凹部４４が設けられており、該
環状凹部４４は、吸気弁Ｖすなわち弁駆動ピストン３７
がその全閉位置から所定量だけ開弁方向に作動したとき
に油圧室４１をダンパ室３６に連通させるべく形成され
る。しかも弁駆動ピストン３７には、油圧室４１に通じ
る環状凹部４４からダンパ室３６への作動油の流通のみ
を許容するチェック弁４２と、環状凹部４４をダンパ室
３６に連通させるオリフィス４３とが設けられる。On the inner surface of the first cylinder body 35, there is provided an annular recess 44 which is always in communication with the hydraulic chamber 41. The annular recess 44 is provided with an intake valve V, that is, a valve driving piston 37.
Is formed so that the hydraulic chamber 41 communicates with the damper chamber 36 when the valve is operated in the valve opening direction by a predetermined amount from the fully closed position. In addition, the valve drive piston 37 is provided with a check valve 42 that allows only the flow of hydraulic oil from the annular recess 44 communicating with the hydraulic chamber 41 to the damper chamber 36, and an orifice 43 that communicates the annular recess 44 with the damper chamber 36. Can be
【００１９】このような伝動機構３１においては、油圧
室４１の油圧を解放しないときの吸気弁Ｖの全閉状態で
は図２で示す状態にあり、この状態から吸気側動弁カム
２８の回転に応じてカム従動ピストン４０が上方に押上
げられると、油圧室４１で発生した油圧がチェック弁４
２およひオリフィス４３を介してダンパ室３６に導か
れ、そのダンパ室３６の油圧により弁駆動ピストン３７
が下方に押下げられる。而して該弁駆動ピストン３７の
下方への摺動途中で油圧室４１は環状凹部４４を介して
ダンパ室３６に直接連通し、それによりダンパ室３６へ
の油の流入量が大となり、弁駆動ピストン３７はさらに
下方に押下げられ、吸気弁Ｖが弁ばね２６のばね力に抗
して開弁する。In such a transmission mechanism 31, when the hydraulic pressure in the hydraulic chamber 41 is not released, the fully closed state of the intake valve V is in the state shown in FIG. Accordingly, when the cam driven piston 40 is pushed upward, the hydraulic pressure generated in the hydraulic chamber 41 changes to the check valve 4.
2 and the orifice 43 are guided to the damper chamber 36, and the hydraulic pressure in the damper chamber 36 causes the valve driving piston 37
Is pushed down. Thus, during the downward sliding of the valve drive piston 37, the hydraulic chamber 41 communicates directly with the damper chamber 36 via the annular recess 44, whereby the amount of oil flowing into the damper chamber 36 increases, and The drive piston 37 is pushed further downward, and the intake valve V opens against the spring force of the valve spring 26.
【００２０】吸気弁Ｖが全開状態になった後に、吸気側
動弁カム２８による押圧力が解除されると、吸気弁Ｖは
弁ばね２６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Ｖの閉弁作動により弁駆動ピストン
３７も上方に押上げられ、ダンパ室３６の油は油圧室４
１に戻される。而して吸気弁Ｖの閉弁作動途中で環状凹
部４４およびダンパ室３６間の直接の連通状態が解除さ
れ、ダンパ室３６および環状凹部４４間にオリフィス４
３が介在するようになると、ダンパ室３６から環状凹部
４４すなわち油圧室４１への油の戻り量が制限される。
このため、吸気弁Ｖ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Ｖが緩やかに着
座することにより、着座時の衝撃が緩和される。When the pressing force of the intake valve cam 28 is released after the intake valve V is fully opened, the intake valve V is driven upward, that is, in the valve closing direction by the spring force of the valve spring 26. The valve drive piston 37 is also pushed upward by the closing operation of the intake valve V, and the oil in the damper chamber 36 is released from the hydraulic chamber 4
Returned to 1. Thus, the direct communication between the annular recess 44 and the damper chamber 36 is released during the closing operation of the intake valve V, and the orifice 4 between the damper chamber 36 and the annular recess 44 is released.
When 3 is interposed, the amount of oil returned from the damper chamber 36 to the annular recess 44, that is, the hydraulic chamber 41 is limited.
For this reason, the upward moving speed of the intake valve V, that is, the valve closing speed is relaxed during the valve closing operation, and the intake valve V is seated gently, so that the impact at the time of seating is reduced.
【００２１】また支持ブロック３４には、吸気弁Ｖが完
全に閉弁した状態で該吸気弁Ｖの上端を検出するリフト
センサＳが配設される。The support block 34 is provided with a lift sensor S for detecting the upper end of the intake valve V when the intake valve V is completely closed.
【００２２】上記伝動機構３１における油圧室４１の油
圧を、吸気弁Ｖの開弁作動途中で解放すると、油圧室４
１は弁ばね２６のばね力に打勝って吸気弁Ｖを開弁し続
けるだけの伝達機能を失うことになり、吸気側動弁カム
２８がリフタ３９を上方に押続けるにもかかわらず、吸
気弁Ｖは前記油圧解放時から弁ばね２６の弾発力により
閉弁作動を開始し、油圧室４１の容積は縮小する。When the hydraulic pressure in the hydraulic chamber 41 of the transmission mechanism 31 is released during the opening of the intake valve V, the hydraulic chamber 4 is released.
1 loses the transmission function of overcoming the spring force of the valve spring 26 and continuing to keep the intake valve V open. The valve V starts the valve closing operation by the resilient force of the valve spring 26 from the release of the hydraulic pressure, and the volume of the hydraulic chamber 41 is reduced.
【００２３】油圧回路３２は、上述の油圧室４１からの
油圧の解放および油圧室４１への作動油の給油を司どる
ものであり、油圧解放弁４５と、アキュムレータ４６
と、一方向弁４７と、チェック弁４８とを有して支持ブ
ロック３４に配設される。The hydraulic circuit 32 controls the release of the hydraulic pressure from the hydraulic chamber 41 and the supply of hydraulic oil to the hydraulic chamber 41. The hydraulic circuit 32 includes a hydraulic release valve 45 and an accumulator 46.
, A one-way valve 47 and a check valve 48 and are disposed on the support block 34.
【００２４】油圧解放弁４５は、油圧室４１に連通して
支持ブロック３４に穿設された油路４９と、アキュムレ
ータ４６に連通しながら支持ブロック３４に穿設された
油路５０との間に介設される電磁弁である。一方向弁４
７は、前記油路５０および油路４９間で、前記油圧解放
弁４５を迂回して支持ブロック３４に配設されるもので
あり、油路５０の油圧が油路４９の油圧よりも設定圧以
上大きくなったときに開弁してアキュムレータ４６から
油路４９すなわち油圧室４１に向けての油の流通のみを
許容するものである。チェック弁４８は、アキュムレー
タ４６と一方向弁４７との中間部すなわち油路５０と、
専用給油路１９との間に介設され、専用給油路１９から
油路５０側への作動油の流通のみを許容するものであ
る。The hydraulic release valve 45 is provided between an oil passage 49 formed in the support block 34 in communication with the hydraulic chamber 41 and an oil passage 50 formed in the support block 34 while communicating with the accumulator 46. It is a solenoid valve interposed. One-way valve 4
7 is disposed on the support block 34 between the oil passage 50 and the oil passage 49 so as to bypass the oil pressure release valve 45, and the oil pressure in the oil passage 50 is set to be higher than the oil pressure in the oil passage 49. When it becomes larger, the valve is opened to allow only the flow of oil from the accumulator 46 to the oil passage 49, that is, the hydraulic chamber 41. The check valve 48 includes an intermediate portion between the accumulator 46 and the one-way valve 47, that is, an oil passage 50,
It is interposed between the dedicated oil supply passage 19 and allows only the flow of hydraulic oil from the dedicated oil supply passage 19 to the oil passage 50 side.
【００２５】ところで、吸気弁Ｖの開弁作動途中で油圧
解放弁４５により油圧室４１の油圧を解放したときに、
次の開弁作動開始までにアキュムレータ４６の油圧は一
方向弁４７を介して油圧室４１に戻され、不足分がチェ
ック弁４８を介して油圧室４１に補給される。而してチ
ェック弁４８を介して油路５０に作用する油圧は、一方
向弁４７の開弁圧である下限圧と、アキュムレータ４６
の蓄圧開始圧である上限圧との間に在ることが必要であ
り、そのような範囲となるように油圧が調圧弁１８によ
り調圧される。When the hydraulic pressure in the hydraulic chamber 41 is released by the hydraulic release valve 45 during the opening operation of the intake valve V,
By the start of the next valve opening operation, the hydraulic pressure of the accumulator 46 is returned to the hydraulic chamber 41 via the one-way valve 47, and the shortage is supplied to the hydraulic chamber 41 via the check valve 48. Thus, the hydraulic pressure acting on the oil passage 50 via the check valve 48 includes the lower limit pressure, which is the valve opening pressure of the one-way valve 47, and the accumulator 46.
It is necessary to be between the upper limit pressure, which is the pressure accumulation start pressure, and the oil pressure is adjusted by the pressure adjusting valve 18 so as to fall within such a range.
【００２６】図３に特に注目して、オイルバス１４は、
カムジャーナル部１２およびカムシャワー部１３・・・
等の動弁系における各潤滑部から漏出した油、ならびに
通路１５から供給される油を一定量貯留すべくシリンダ
ヘッド１１に設けられるものであり、第２オイルポンプ
ＰＣ に接続された吸入管５１が該オイルバス１４内に
突入され、該吸入管５１の先端にはストレーナ５２が設
けられる。またシリンダヘッド１１には、オイルバス１
４からの余剰の油をオイルパン１に戻すための複数の溢
流管５３が設けられている。さらにシリンダヘッド１１
の下部には、オイルバス１４内の油を抜き出すためのプ
ラグ５４が螺合されている。With particular attention to FIG. 3, the oil bath 14
Cam journal section 12 and cam shower section 13 ...
Oil leaked from the lubricating portion in the valve system and the like, and are those provided in the cylinder head 11 so as to a certain amount storing oil supplied from the passage 15, the suction tube connected to the second oil pump P C 51 is protruded into the oil bath 14, and a strainer 52 is provided at the tip of the suction pipe 51. The cylinder head 11 has an oil bath 1
A plurality of overflow pipes 53 for returning excess oil from the oil pan 4 to the oil pan 1 are provided. Further, the cylinder head 11
A plug 54 for extracting oil from the oil bath 14 is screwed to a lower portion of the oil bath 14.
【００２７】シリンダヘッド１１に配設された動弁系等
を覆うようにしてシリンダヘッド１１の上部にはヘッド
カバー５５が結着されており、このヘッドカバー５５に
は、オイルバス１４の直上に位置するようにして給油口
５６が設けられ、該給油口５６はオイルキャップ５７で
開閉可能に閉塞される。A head cover 55 is attached to an upper portion of the cylinder head 11 so as to cover a valve operating system and the like provided on the cylinder head 11. The head cover 55 is located immediately above the oil bath 14. Thus, the oil supply port 56 is provided, and the oil supply port 56 is closed by the oil cap 57 so as to be openable and closable.
【００２８】次にこの実施例の作用について説明する
と、弁作動特性変更手段２１において、吸気弁Ｖの開弁
作動途中に油圧解放弁４５を開弁したときに油圧室４１
の油圧はアキュムレータ４６に逃がされるものであり、
油圧解放弁４５の開弁時期すなわち油圧解放時期を制御
することにより、吸気弁Ｖの開閉作動特性を変更するこ
とができる。すなわち図４で示すように、吸気弁Ｖのリ
フト量および閉弁時期が油圧解放時期の制御により無段
階に変化せしめられるものであり、機関負荷が大きくな
るにつれて吸気弁Ｖの作動特性は曲線ａ→ｂ→ｃ→ｄ→
ｅ→ｆと変化していく。Next, the operation of this embodiment will be described. In the valve operating characteristic changing means 21, when the hydraulic release valve 45 is opened during the opening operation of the intake valve V, the hydraulic chamber 41 is opened.
Is released to the accumulator 46,
By controlling the valve opening timing of the hydraulic release valve 45, that is, the hydraulic release timing, the opening / closing operation characteristics of the intake valve V can be changed. That is, as shown in FIG. 4, the lift amount and the valve closing timing of the intake valve V can be steplessly changed by controlling the hydraulic pressure release timing. As the engine load increases, the operating characteristic of the intake valve V becomes a curve a. → b → c → d →
It changes from e to f.
【００２９】また第２オイルポンプＰC は、シリンダヘ
ッド１１に設けられたオイルバス１４から作動油を汲上
げるべくシリンダヘッド１１に配設されるものであり、
弁作動特性変更手段２１の油圧室４１および第２オイル
ポンプＰC 間の距離を比較的短くすることができ、した
がって、機関の始動時には、弁作動特性変更手段２１の
油圧室４１への給油を速やかに行なって応答性を向上す
ることができる。Further second oil pump P C is intended to be disposed hydraulic oil to the cylinder head 11 Beku pumping gel from the oil bath 14 provided in the cylinder head 11,
Valve operating characteristic changing means can be relatively short distance between the hydraulic chamber 41 of the 21 and the second oil pump P C, therefore, at the time of start of the engine, the oil supply to the hydraulic chamber 41 of the valve operating characteristic changing means 21 This can be performed promptly to improve responsiveness.
【００３０】ところで、弁作動特性変更手段２１で必要
な油量は図５で示すように機関負荷に応じて変化するも
のである。すなわち低負荷領域ＲL では、図４で示した
ように油圧室４１の油圧解放時期を早めて弁リフト量を
小さくするとともに閉弁時期を早めるので必要油量が多
くなるものであり、特に機関始動時には必要油量が多く
なる。また機関負荷が高くなるにつれて前記油圧解放時
期が遅くなることにより必要油量が低下するものであ
り、高負荷領域ＲH では、吸気弁Ｖが全閉状態にあると
きに作動油の冷却および新鮮な作動油との交換を果たす
べく油圧室４１の作動油を抜くのみであるので、一定か
つ少量の作動油が必要となるだけであり、必要油量は最
低になる。The amount of oil required by the valve operating characteristic changing means 21 varies according to the engine load as shown in FIG. That is, in the low load region RL , as shown in FIG. 4, the oil release time of the hydraulic chamber 41 is advanced to shorten the valve lift amount and the valve closing time is advanced, so that the required oil amount is increased. At the time of starting, the required oil amount increases. Further, as the engine load increases, the required oil amount decreases due to the delay of the hydraulic pressure release timing. In the high load region RH , when the intake valve V is in the fully closed state, cooling of the hydraulic oil and fresh Since only the hydraulic oil in the hydraulic chamber 41 is drained in order to exchange the hydraulic oil with another hydraulic oil, only a constant and small amount of hydraulic oil is required, and the required oil amount is minimized.
【００３１】このように弁作動特性変更手段２１で必要
な油量は機関負荷に応じて変化するが、第２オイルポン
プＰC は弁作動特性変更手段２１専用のものであり、他
の潤滑部等とは無関係にポンプ容量を設定可能である。
このため、機関の運転状態に対応した弁作動特性変更手
段２１の必要油量に応じて第２オイルポンプＰC の吐出
量を設定していても、他の潤滑部等への給油量に影響を
及ぼすことはなく、機関高速運転時にフリクションロス
が大きくなることはない。[0031] This amount of oil required in the valve operating characteristic changing means 21 so as to vary in accordance with the engine load, the second oil pump P C is of only the valve operating characteristic changing means 21, other lubrication The pump capacity can be set independently of the above.
Therefore, even if you set the discharge amount of the second oil pump P C in accordance with the required oil amount of the valve operating characteristic changing means 21 corresponding to the operating state of the engine, affecting the quantity of oil to other lubrication, etc. The friction loss does not increase during high-speed operation of the engine.
【００３２】さらにオイルバス１４とオイルパン１とは
相互に連通しているので、潤滑用給油系ＯL および弁作
動特性変更手段用給油系ＯV のオイル交換および補給等
のメンテナンスを両給油系ＯL ，ＯV で独立して行なう
ことが不要である。すなわちオイルバス１４の直上にあ
る給油口５６から油を供給することにより、油がオイル
バス１４から溢流管５３を経てオイルパン１に流れるこ
とになり、オイルバス１４およびオイルパン１への給油
を１回で行なうことができてメンテナンス作業が容易と
なる。この際、オイルバス１４には確実に一定量の油が
貯留されることになるので、第２オイルポンプＰC がエ
アーを吸い込んで作動不良を生じることは確実に防止さ
れる。Furthermore since the oil bath 14 and the oil pan 1 communicates with each other, both the fuel supply system maintenance oil change and makeup, etc. of the lubrication oil supply system O L, and the valve operating characteristic changing means for refueling system O V It is not necessary to carry out independently at O L and O V. That is, by supplying the oil from the oil supply port 56 located immediately above the oil bath 14, the oil flows from the oil bath 14 to the oil pan 1 via the overflow pipe 53, and the oil is supplied to the oil bath 14 and the oil pan 1. Can be performed once, and maintenance work becomes easy. At this time, since surely certain amount of oil in the oil bath 14 is to be stored, the second oil pump P C results in a malfunction inhale air is reliably prevented.
【００３３】しかもオイルバス１４には、カムジャーナ
ル部１２およびカムシャワー部１３・・・等の動弁系に
おける各潤滑部から漏出した油だけでなく、動弁系潤滑
用分岐油路７からの油が通路１５を介して機関作動時に
常時供給されているので、前記漏出による油量が比較的
少なくてもオイルバス１４への油の安定的な補給が可能
である。Further, the oil bath 14 contains not only oil leaked from each lubricating portion in the valve train such as the cam journal portion 12 and the cam shower portion 13. Since the oil is always supplied through the passage 15 when the engine is operating, the oil can be stably supplied to the oil bath 14 even if the oil amount due to the leakage is relatively small.
【００３４】図６は本発明の他の実施例を示すものであ
り、上記実施例に対応する部分には同一の参照符号を付
す。FIG. 6 shows another embodiment of the present invention, in which parts corresponding to the above-mentioned embodiment are denoted by the same reference numerals.
【００３５】ヘッドカバー５５に設けられた給油口５６
がオイルバス１４の直上位置からずれて配置される場合
もあり、この場合には、該給油口５６の下方を覆うよう
にしてカバー５８がヘッドカバー５５に固定され、該カ
バー５８には、前記給油口５６から給油された油をヘッ
ドカバー５５内に導入する導入口５９が設けられ、該導
入口５９はオイルバス１４の直上位置に配設される。Oil supply port 56 provided in head cover 55
In some cases, the cover 58 is fixed to the head cover 55 so as to cover the lower portion of the oil supply port 56, and the cover 58 An introduction port 59 for introducing oil supplied from the port 56 into the head cover 55 is provided, and the introduction port 59 is disposed immediately above the oil bath 14.
【００３６】このようにすれば、上記実施例と同様に、
給油口５６から供給される油をカバー５８によって導入
口５９に導き、該導入口５９からオイルバス１４に油を
確実に供給することができる。In this way, similar to the above embodiment,
The oil supplied from the oil supply port 56 is guided to the introduction port 59 by the cover 58, and the oil can be reliably supplied to the oil bath 14 from the introduction port 59.
【００３７】以上の各実施例では、機関弁として吸気弁
を取り上げて説明したが、本発明を機関弁としての排気
弁に関連して実施することも可能である。In each of the above embodiments, the intake valve has been described as an engine valve. However, the present invention can be implemented in connection with an exhaust valve as an engine valve.
【００３８】[0038]
【発明の効果】以上のように請求項１・２の各発明によ
れば、機関本体の下部に設けられたオイルパンから作動
油を汲み上げる第１オイルポンプには作動油消費部に通
じる給油路が接続され、クランク軸に連なる動弁カム軸
を含む動弁系の各潤滑部に通じる動弁系潤滑用分岐油路
が前記給油路から分岐され、シリンダヘッドには、前記
動弁系の各潤滑部から漏出した油を受容可能であるとと
もに前記オイルパンに余剰油を溢流可能なオイルバスが
設けられ、該オイルバスから作動油を汲上げる第２オイ
ルポンプが前記弁作動特性変更手段の油圧室に接続され
るので、第２オイルポンプの容量を他の潤滑部で必要な
油量とは無関係に設定して、機関高速回転時のフリクシ
ョンロスの増大を抑えることができ、しかもオイルバス
およびオイルパンが連通していることによりメンテナン
ス作業を簡略化することができる。As described above, according to the first and second aspects of the present invention , the first oil pump for pumping hydraulic oil from the oil pan provided at the lower part of the engine body has an oil supply passage communicating with the hydraulic oil consuming portion. Are connected, a valve operating system lubricating branch oil passage communicating with each lubricating portion of the valve operating system including the valve operating cam shaft connected to the crankshaft is branched from the oil supply passage, and a cylinder head is provided with each of the valve operating systems. An oil bath capable of receiving the oil leaked from the lubricating portion and allowing the excess oil to overflow into the oil pan is provided, and a second oil pump for pumping hydraulic oil from the oil bath is provided with a valve operating characteristic changing means. Since it is connected to the hydraulic chamber, the capacity of the second oil pump can be set independently of the amount of oil required in the other lubricating parts, and increase in friction loss during high-speed rotation of the engine can be suppressed. And oil pan It is possible to simplify the maintenance work by in communication.
【００３９】また特に請求項１の発明によれば、動弁系
潤滑用分岐油路には、オイルバスに直接通じる通路が接
続されるので、機関作動時にはオイルポンプからオイル
バスに常時油を供給するようにしてオイルバスへの油の
補給を安定化することができる。According to the first aspect of the present invention , since the branch oil passage for lubricating the valve train is connected to a passage directly communicating with the oil bath, the oil is always supplied from the oil pump to the oil bath when the engine is operating. As a result, the supply of oil to the oil bath can be stabilized.
【００４０】また特に請求項２の発明によれば、シリン
ダヘッドに結着されるヘッドカバーに設けられる給油口
あるいは該給油口に通じる導入口が、オイルバスの直上
に配設されるので、給油口からの給油時にオイルバスに
油を確実に貯留することができ、エアー吸込みを防止し
て第２オイルポンプの作動を円滑にすることができる。According to the second aspect of the present invention , the oil supply port provided in the head cover connected to the cylinder head or the introduction port communicating with the oil supply port is disposed immediately above the oil bath. The oil can be reliably stored in the oil bath at the time of refueling, and the suction of air can be prevented to make the operation of the second oil pump smooth.
【図１】本発明の一実施例の機関本体の給油系統図であ
る。FIG. 1 is an oil supply system diagram of an engine body according to an embodiment of the present invention.
【図２】弁作動特性変更手段の構成を示す縦断面図であ
る。FIG. 2 is a longitudinal sectional view showing a configuration of a valve operating characteristic changing means.
【図３】図２の３−３線に沿うシリンダヘッドの断面図
である。FIG. 3 is a sectional view of the cylinder head taken along line 3-3 in FIG. 2;
【図４】機関弁の作動特性図である。FIG. 4 is an operation characteristic diagram of an engine valve.
【図５】機関負荷に対する弁作動特性変更手段の必要油
量特性図である。FIG. 5 is a characteristic diagram of a required oil amount of a valve operating characteristic changing means with respect to an engine load.
【図６】本発明の他の実施例の図２に対応した断面図で
ある。FIG. 6 is a sectional view corresponding to FIG. 2 of another embodiment of the present invention.
１ オイルパン ５ 給油路 ７ 動弁系潤滑用分岐油路 ８，９ 作動油消費部 １１ シリンダヘッド １２，１３ 潤滑部 １４ オイルバス １５ 通路 ２１ 弁作動特性変更手段 ２７ 動弁カム軸 ４１ 油圧室 ５５ ヘッドカバー ５６ 給油口 ５９ 導入口 Ｅ 機関本体 Ｖ 機関弁としての吸気弁 Ｐ 第１オイルポンプ ＰC 第２オイルポンプDESCRIPTION OF SYMBOLS 1 Oil pan 5 Oil supply path 7 Branch oil path for valve system lubrication 8, 9 Hydraulic oil consumption section 11 Cylinder head 12, 13 Lubrication section 14 Oil bath 15 Passage 21 Valve operation characteristic changing means 27 Valve camshaft 41 Hydraulic chamber 55 head cover 56 intake valve P first oil pump P C second oil pump as oil supply port 59 inlet E engine body V engine valve
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ Ｆ０１Ｍ 11/02 Ｆ０１Ｍ 11/02 Ｆ０２Ｄ 13/02 Ｆ０２Ｄ 13/02 Ｇ Ｆ０２Ｆ 1/24 Ｆ０２Ｆ 1/24 Ｇ (56)参考文献 実開 昭60−4705（ＪＰ，Ｕ) 実開 昭61−179311（ＪＰ，Ｕ) 実開 昭63−138407（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F01M 1/06 F01L 13/00 301 F01M 1/02 F01M 11/02 F02D 13/02 ────────────────────────────────────────────────── ─── Continued on the front page (51) Int.Cl. 7 Identification code FI F01M 11/02 F01M 11/02 F02D 13/02 F02D 13/02 G F02F 1/24 F02F 1/24 G (56) References Actual 60-1705 (JP, U) Full opening 61-177931 (JP, U) Full opening 63-138407 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F01M 1 / 06 F01L 13/00 301 F01M 1/02 F01M 11/02 F02D 13/02
Claims (2)
に支持された機関弁（Ｖ）およびクランク軸間に、油圧
室（４１）の油圧変化に応じて前記機関弁（Ｖ）の作動
特性を変更可能な弁作動特性変更手段（２１）が介設さ
れて成る動弁装置を備えた内燃機関において、機関本体
（Ｅ）の下部に設けられたオイルパン（１）から作動油
を汲み上げる第１オイルポンプ（Ｐ）には作動油消費部
（８，９）に通じる給油路（５）が接続され、クランク
軸に連なる動弁カム軸（２７）を含む動弁系の各潤滑部
（１２，１３）に通じる動弁系潤滑用分岐油路（７）が
前記給油路（５）から分岐され、シリンダヘッド（１
１）には、前記動弁系の各潤滑部（１２，１３）から漏
出した油を受容可能であるとともに前記オイルパン
（１）に余剰油を溢流可能なオイルバス（１４）が設け
られ、該オイルバス（１４）から作動油を汲上げる第２
オイルポンプ（ＰC ）が前記弁作動特性変更手段（２
１）の油圧室（４１）に接続され、前記動弁系潤滑用分
岐油路（７）には、オイルバス（１４）に直接通じる通
路（１５）が接続されることを特徴とする、内燃機関に
おける給油装置。An operating characteristic of said engine valve (V) is changed between an engine valve (V) supported on a cylinder head (11) so as to be capable of opening and closing and a crankshaft according to a change in oil pressure in a hydraulic chamber (41). In an internal combustion engine provided with a valve operating device having variable valve operating characteristic changing means (21) interposed therein, a first oil pump for pumping hydraulic oil from an oil pan (1) provided at a lower portion of the engine body (E). An oil pump (P) is connected to an oil supply passage (5) leading to a hydraulic oil consuming unit (8, 9), and each lubrication unit (12, 12) of a valve train including a valve train camshaft (27) connected to a crankshaft. 13) A branching oil passage (7) for valve system lubrication leading to the oil supply passage (5) is branched from the oil supply passage (5) and
1) is provided with an oil bath (14) capable of receiving oil leaked from each lubricating portion (12, 13) of the valve train and capable of overflowing surplus oil into the oil pan (1). A second pumping operation oil from the oil bath (14).
The oil pump (P C ) is provided with the valve operating characteristic changing means (2).
Is connected to 1) the hydraulic pressure chamber (41), said valve train lubrication min
The oil passage (7) has a direct connection to the oil bath (14).
A refueling device for an internal combustion engine, characterized in that a road (15) is connected .
に支持された機関弁（Ｖ）およびクランク軸間に、油圧
室（４１）の油圧変化に応じて前記機関弁（Ｖ）の作動
特性を変更可能な弁作動特性変更手段（２１）が介設さ
れて成る動弁装置を備えた内燃機関において、機関本体
（Ｅ）の下部に設けられたオイルパン（１）から作動油
を汲み上げる第１オイルポンプ（Ｐ）には作動油消費部
（８，９）に通じる給油路（５）が接続され、クランク
軸に連なる動弁カム軸（２７）を含む動弁系の各潤滑部
（１２，１３）に通じる動弁系潤滑用分岐油路（７）が
前記給油路（５）から分岐され、シリンダヘッド（１
１）には、前記動弁系の各潤滑部（１２，１３）から漏
出した油を受容可能であるとともに前記オイルパン
（１）に余剰油を溢流可能なオイルバス（１４）が設け
られ、該オイルバス（１４）から作動油を汲上げる第２
オイルポンプ（Ｐ C ）が前記弁作動特性変更手段（２
１）の油圧室（４１）に接続され、シリンダヘッド（１
１）に結着されるヘッドカバー（５５）に設けられる給
油口（５６）あるいは該給油口（５６）に通じる導入口
（５９）が、前記オイルバス（１４）の直上に配設され
ることを特徴とする、内燃機関における給油装置。2. The opening and closing operation of the cylinder head (11) is possible.
Between the engine valve (V) and the crankshaft
Actuation of the engine valve (V) in response to a change in oil pressure in the chamber (41)
A valve operating characteristic changing means (21) capable of changing characteristics is provided.
An internal combustion engine provided with a valve operating device comprising:
Hydraulic oil from the oil pan (1) provided at the lower part of (E)
The first oil pump (P) that pumps oil
The oil supply passage (5) leading to (8, 9) is connected
Each lubrication unit of the valve train including the valve train camshaft (27) connected to the shaft
The branch oil passage (7) for valve system lubrication leading to (12, 13)
The cylinder head (1) is branched from the oil supply passage (5).
1) leaks from each lubrication part (12, 13) of the valve train.
The oil pan,
(1) Oil bath (14) is provided to allow excess oil to overflow
A second pumping operation oil from the oil bath (14).
The oil pump (P C ) is provided with the valve operating characteristic changing means (2).
The cylinder head (1 ) is connected to the hydraulic chamber (41) of the cylinder head (1).
An oil supply port (56) provided in a head cover (55) attached to 1) or an introduction port (59) leading to the oil supply port (56) is arranged directly above the oil bath (14). A refueling device for an internal combustion engine , characterized by :
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2408255A JP3023803B2 (en) | 1990-12-27 | 1990-12-27 | Oil supply device for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2408255A JP3023803B2 (en) | 1990-12-27 | 1990-12-27 | Oil supply device for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04228815A JPH04228815A (en) | 1992-08-18 |
| JP3023803B2 true JP3023803B2 (en) | 2000-03-21 |
Family
ID=18517735
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2408255A Expired - Fee Related JP3023803B2 (en) | 1990-12-27 | 1990-12-27 | Oil supply device for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3023803B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004076825A1 (en) * | 2003-02-28 | 2004-09-10 | Aisin Seiki Kabushiki Kaisha | Oil-feeding device for engine |
| CN100562649C (en) * | 2003-02-28 | 2009-11-25 | 爱信精机株式会社 | Oil-feeding device for engine |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5915348A (en) * | 1996-11-07 | 1999-06-29 | Ina Walzlager Schaeffler Ohg | Adjusting cylinder of a camshaft adjusting device acted upon by a separate oil supply unit |
| DE19604865B4 (en) * | 1996-02-10 | 2009-05-07 | Schaeffler Kg | Actuating cylinder of a camshaft adjuster which can be acted upon by a separate oil delivery device |
| JP4609714B2 (en) * | 2005-05-19 | 2011-01-12 | アイシン精機株式会社 | Valve timing control device |
| WO2007073770A1 (en) * | 2005-12-27 | 2007-07-05 | Renault Trucks | Lubrication system and internal combustion engine comrising such a system |
| JP2017180171A (en) * | 2016-03-29 | 2017-10-05 | マツダ株式会社 | Oil supply device of engine |
| JP6409809B2 (en) * | 2016-03-30 | 2018-10-24 | マツダ株式会社 | Engine oil supply device |
| GB2551602B (en) * | 2016-06-20 | 2020-10-28 | Ford Global Tech Llc | An engine assembly with improved oil pressure regulation |
| JP6414150B2 (en) * | 2016-06-30 | 2018-10-31 | マツダ株式会社 | Engine oil supply device |
-
1990
- 1990-12-27 JP JP2408255A patent/JP3023803B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004076825A1 (en) * | 2003-02-28 | 2004-09-10 | Aisin Seiki Kabushiki Kaisha | Oil-feeding device for engine |
| CN100562649C (en) * | 2003-02-28 | 2009-11-25 | 爱信精机株式会社 | Oil-feeding device for engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04228815A (en) | 1992-08-18 |
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| LAPS | Cancellation because of no payment of annual fees |