JPH07253054A - Exhaust gas recirculation device of engine - Google Patents
Exhaust gas recirculation device of engineInfo
- Publication number
- JPH07253054A JPH07253054A JP6043507A JP4350794A JPH07253054A JP H07253054 A JPH07253054 A JP H07253054A JP 6043507 A JP6043507 A JP 6043507A JP 4350794 A JP4350794 A JP 4350794A JP H07253054 A JPH07253054 A JP H07253054A
- Authority
- JP
- Japan
- Prior art keywords
- port
- exhaust gas
- valve
- exhaust
- gas recirculation
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/16—Indirect injection
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、エンジンの排気ガス
中のＮＯX を低減させる排ガス再循環装置（以下、ＥＧ
Ｒ装置という）に関し、特に排ガス還流通路の配管を不
要にして、コスト低減を図る技術に関する。BACKGROUND OF THE INVENTION This invention is an exhaust gas recirculation apparatus for reducing NO X in the exhaust gas of the engine (hereinafter, EG
R device), and particularly to a technique for reducing costs by eliminating the need for piping in the exhaust gas recirculation passage.
【０００２】[0002]
【従来の技術】この種のＥＧＲ装置としては、従来より
例えば図３中符号１０で示すものがある。それはエンジ
ンＥの吸気ポート４と排気ポート５とをＥＧＲ制御弁１
２を有する排ガス還流通路１１で連通して構成されてい
る。この従来例はシリンダヘッド２の外に排ガス還流通
路１１を配管して構成されている。このＥＧＲ装置１０
を付設することにより、排気ガスを吸気に還流させてＮ
ＯX の排出を低減させ、最高燃焼温度を下げるのに最も
効果的である。2. Description of the Related Art As an EGR device of this type, there is a conventional device shown by reference numeral 10 in FIG. It connects the intake port 4 and the exhaust port 5 of the engine E to the EGR control valve 1
An exhaust gas recirculation passage 11 having two is connected to each other. In this conventional example, an exhaust gas recirculation passage 11 is arranged outside the cylinder head 2. This EGR device 10
By attaching an exhaust gas, the exhaust gas is returned to the intake air and N
O X emissions is reduced, and is most effective in lowering the maximum combustion temperature.
【０００３】なお、このエンジンＥは一部油冷式強制空
冷ディーゼルエンジンであり、フライホイルファン２１
で起こした冷却風Ａを、ファンケース２２で案内して、
シリンダの外周、シリンダヘッド２に形成されたトンネ
ル式冷却風路３、及び放熱器２０に向けて分流させるよ
うに構成されている。また、シリンダヘッド２内の副燃
焼室８の外周には油冷室９が形成され、潤滑油がオイル
パンから油冷室９に圧送されて副燃焼室８を冷却し、放
熱器２０を経て放熱し、再びオイルパンへ還流するよう
に構成されている。Incidentally, the engine E is a partially oil-cooled forced air-cooled diesel engine, and the flywheel fan 21
Guide the cooling air A generated in step 2 with the fan case 22,
The flow is divided toward the outer periphery of the cylinder, the tunnel-type cooling air passage 3 formed in the cylinder head 2, and the radiator 20. Further, an oil cooling chamber 9 is formed on the outer periphery of the sub combustion chamber 8 in the cylinder head 2, and lubricating oil is pumped from the oil pan to the oil cooling chamber 9 to cool the sub combustion chamber 8 and pass through the radiator 20. The heat is radiated and the oil is returned to the oil pan again.
【０００４】[0004]
【発明が解決しようとする課題】上記従来例では、エン
ジンＥの吸気ポート４と排気ポート５とを連通する排ガ
ス還流通路１１が、シリンダヘッド２の外に配管されて
いることから、その配管のための部品点数が増え、コス
ト低減を図るうえで障害になる。また、この種のＥＧＲ
装置によれば、還流排気ガスにより吸気を暖めて冷始動
後のエンジンの暖機運転を促進するとともに、白煙の発
生を抑制することができるが、上記従来例の配管構造で
は、排ガス還流通路１１を流通する間に還流排気ガスの
温度が大幅に低下するため、エンジンの暖機運転を促進
し、白煙の発生を抑制するうえで障害になる。本発明は
このような事情を考慮してなされたもので、 上記配管を無くして部品点数の削減とコスト低減を
図ること、 冷始動後の暖機運転の促進と白煙の防止を効果的に
達成すること、を技術課題とする。In the above-mentioned conventional example, the exhaust gas recirculation passage 11 that connects the intake port 4 and the exhaust port 5 of the engine E is piped outside the cylinder head 2. As a result, the number of parts used for this purpose increases, which is an obstacle to cost reduction. Also, this kind of EGR
According to the device, it is possible to warm the intake air with the recirculated exhaust gas to accelerate the warm-up operation of the engine after the cold start and suppress the generation of white smoke. Since the temperature of the recirculated exhaust gas is drastically reduced while flowing through 11, it is an obstacle in promoting warm-up operation of the engine and suppressing generation of white smoke. The present invention has been made in consideration of such circumstances, and effectively eliminates the above-mentioned piping to reduce the number of parts and costs, promotes warm-up operation after cold start and prevents white smoke. Achievement is a technical issue.
【０００５】[0005]
【課題を解決するための手段】上記課題を解決するため
に、請求項１の発明が採用した手段は、エンジンＥの吸
気ポート４と排気ポート５とをＥＧＲ制御弁１２を有す
る排ガス還流通路１１で連通して構成したエンジンの排
ガス再循環装置において、上記吸気ポート４は、吸気弁
口４ａからシリンダヘッド２の横一側に導出し、排気ポ
ート５は吸気ポート４と略直交するように排気弁口５ａ
からシリンダヘッド２の後方横一側に導出し、上記吸気
弁口４ａと排気弁口５ａとの間の弁口間肉壁６に上記排
ガス還流通路１１を貫通形成して上記吸気弁口４ａと排
気弁口５ａとを上記排ガス還流通路１１で連通し、この
排ガス還流通路１１にＥＧＲ制御弁１２を構成する弁軸
１３を装着して構成したことを特徴とする。In order to solve the above-mentioned problems, the means adopted by the invention of claim 1 is the exhaust gas recirculation passage 11 having the EGR control valve 12 for the intake port 4 and the exhaust port 5 of the engine E. In the exhaust gas recirculation system for an engine configured to communicate with each other, the intake port 4 is led out to one lateral side of the cylinder head 2 from the intake valve port 4a, and the exhaust port 5 is exhausted so as to be substantially orthogonal to the intake port 4. Valve 5a
To the rear lateral one side of the cylinder head 2, and the exhaust gas recirculation passage 11 is formed through the inter-valve wall 6 between the intake valve opening 4a and the exhaust valve opening 5a to form the intake valve opening 4a. The exhaust valve recirculation passage 11 communicates with the exhaust valve port 5a, and the exhaust gas recirculation passage 11 is equipped with a valve shaft 13 constituting an EGR control valve 12.
【０００６】請求項２の発明が採用した手段は、エンジ
ンＥの吸気ポート４と排気ポート５とをＥＧＲ制御弁１
２を有する排ガス還流通路１１で連通して構成したエン
ジンの排ガス再循環装置において、上記吸気ポート４の
吸気弁口４ａと排気ポート５の排気弁口５ａとの間の弁
口間肉壁６にシリンダヘッド２の頂部側よりキリ孔１９
ａをあけ、このキリ孔１９ａにＥＧＲ制御弁１２を構成
する弁軸１３を装着し、この弁軸１３に開口１４をあけ
て上記排ガス還流通路１１を形成し、上記吸気弁口４ａ
と排気弁口５ａとを上記排ガス還流通路１１で連通して
構成したことを特徴とする。According to a second aspect of the present invention, the EGR control valve 1 connects the intake port 4 and the exhaust port 5 of the engine E.
In an exhaust gas recirculation system for an engine, which is configured to communicate with an exhaust gas recirculation passage 11 having two, the inter-valve wall 6 between the intake valve port 4a of the intake port 4 and the exhaust valve port 5a of the exhaust port 5 is provided. Drilling hole 19 from the top side of the cylinder head 2
a, a valve shaft 13 constituting the EGR control valve 12 is attached to the drill hole 19a, an opening 14 is opened in the valve shaft 13 to form the exhaust gas recirculation passage 11, and the intake valve port 4a is formed.
And the exhaust valve port 5a are communicated with each other through the exhaust gas recirculation passage 11.
【０００７】請求項３の発明が採用した手段は、エンジ
ンＥの吸気ポート４と排気ポート５とをＥＧＲ制御弁１
２を有する排ガス還流通路１１で連通して構成したエン
ジンの排ガス再循環装置において、上記吸気ポート４
は、吸気弁口４ａからシリンダヘッド２の横一側に導出
し、排気ポート５は吸気ポート４と略直交するように排
気弁口５ａからシリンダヘッド２の後方横一側に導出
し、上記吸気弁口４ａと排気弁口５ａとに隣接させて、
シリンダヘッド２を前後方向へ貫通するトンネル式冷却
風路３を形成し、上記吸気弁口４ａと排気弁口５ａとの
間の弁口間肉壁６を上記トンネル式冷却風路３側へ膨出
させ、上記膨出肉壁部分６ａに上記排ガス還流通路１１
を形成して上記吸気弁口４ａと排気弁口５ａとを上記排
ガス還流通路１１で連通し、この排ガス還流通路１１に
ＥＧＲ制御弁１２を構成する弁軸１３を装着して構成し
たことを特徴とする。According to a third aspect of the invention, the EGR control valve 1 connects the intake port 4 and the exhaust port 5 of the engine E to each other.
In the exhaust gas recirculation device for an engine, which is configured to communicate with each other through the exhaust gas recirculation passage 11 including the intake port 4
Is led out from the intake valve port 4a to one lateral side of the cylinder head 2, and the exhaust port 5 is led out from the exhaust valve port 5a to one lateral side behind the cylinder head 2 so as to be substantially orthogonal to the intake port 4. Adjacent to the valve opening 4a and the exhaust valve opening 5a,
A tunnel-type cooling air passage 3 that penetrates the cylinder head 2 in the front-rear direction is formed, and an inter-valve wall 6 between the intake valve opening 4a and the exhaust valve opening 5a is expanded toward the tunnel-type cooling air passage 3 side. The exhaust gas recirculation passage 11 on the bulging wall portion 6a.
Is formed to connect the intake valve port 4a and the exhaust valve port 5a with each other through the exhaust gas recirculation passage 11, and the exhaust gas recirculation passage 11 is equipped with a valve shaft 13 that constitutes an EGR control valve 12. And
【０００８】[0008]
【発明の作用・効果】請求項１及び請求項２の発明で
は、吸気ポート４の吸気弁口４ａと排気ポート５の排気
弁口５ａとの間の弁口間肉壁６にＥＧＲ制御弁１２を有
する排ガス還流通路１１を形成し、吸気弁口４ａと排気
弁口５ａとを上記排ガス還流通路１１で連通したことか
ら、シリンダヘッド２の外に配管する必要はなく、部品
点数の削減とコスト低減を図ることができる。また、吸
気弁口４ａと排気弁口５ａとは排ガス還流通路１１によ
って最短距離で連通されるので、この排ガス還流通路１
１を流通する間に還流排気ガスの温度が大幅に低下する
ことは避けられる。これにより、冷始動後の暖機運転を
促進し、白煙の発生を効果的に防止することができる。According to the inventions of claims 1 and 2, the EGR control valve 12 is provided on the inter-valve wall 6 between the intake valve port 4a of the intake port 4 and the exhaust valve port 5a of the exhaust port 5. Since the exhaust gas recirculation passage 11 having the above is formed and the intake valve opening 4a and the exhaust valve opening 5a are communicated with each other through the exhaust gas recirculation passage 11, it is not necessary to pipe outside the cylinder head 2, and the number of parts is reduced and the cost is reduced. It can be reduced. Further, since the intake valve port 4a and the exhaust valve port 5a are communicated by the exhaust gas recirculation passage 11 at the shortest distance, the exhaust gas recirculation passage 1
It is possible to prevent the temperature of the recirculated exhaust gas from dropping significantly during the passage of 1. Thereby, the warm-up operation after the cold start can be promoted, and the generation of white smoke can be effectively prevented.
【０００９】請求項３の発明では、上記吸気弁口４ａと
排気弁口５ａとの間の弁口間肉壁６を上記トンネル式冷
却風路３側へ膨出させ、この膨出肉壁部分６ａに上記排
ガス還流通路１１を形成して上記吸気弁口４ａと排気弁
口５ａとを上記排ガス還流通路１１で連通したことか
ら、上記請求項１及び請求項２の発明と同様に、シリン
ダヘッド２の外に配管する必要はなく、部品点数の削減
とコスト低減を図ることができる。また、吸気弁口４ａ
と排気弁口５ａとは排ガス還流通路１１によって短距離
で連通されるので、この排ガス還流通路１１を流通する
間に還流排気ガスの温度が大幅に低下することは避けら
れ、冷始動後のエンジンの暖機運転をさらに促進し、白
煙の発生を効果的に防止することができる。According to the third aspect of the invention, the inter-valve wall 6 between the intake valve port 4a and the exhaust valve port 5a is bulged toward the tunnel cooling air passage 3 side, and this bulged wall portion is formed. Since the exhaust gas recirculation passage 11 is formed in 6a and the intake valve opening 4a and the exhaust valve opening 5a are communicated with each other through the exhaust gas recirculation passage 11, the cylinder head is the same as the invention of claim 1 and claim 2. It is not necessary to provide a pipe outside 2, and the number of parts and cost can be reduced. In addition, the intake valve port 4a
Since the exhaust valve port 5a and the exhaust valve port 5a are communicated with each other by the exhaust gas recirculation passage 11 in a short distance, it is possible to prevent the temperature of the recirculated exhaust gas from significantly decreasing while flowing through the exhaust gas recirculation passage 11, and the engine after the cold start. It is possible to further accelerate the warm-up operation of, and effectively prevent the generation of white smoke.
【００１０】[0010]
【実施例】以下本発明の実施例を図面に基づいてさらに
詳しく説明する。図１は請求項１の発明に係る第１の実
施例を示すディーゼルエンジンの要部横断平面図、図２
は図１のＩ−Ｉ線矢視縦断面図である。このエンジンＥ
は前記従来例と同様に一部油冷式強制空冷の頭上弁ディ
ーゼルエンジンとして構成されている。即ち、このエン
ジンＥは、エンジン本体１の前側に設けたフライホイル
ファン２１及びファンケース２２と、シリンダヘッド２
の前側上部に設けたオイルクーラ（放熱器）２０と、シ
リンダヘッド２に貫通形成したトンネル式冷却風路３
と、油冷室９とを具備して成り、フライホイルファン２
１で起こした冷却風Ａを、ファンケース２２で案内して
シリンダブロック、トンネル式冷却風路３及び放熱器２
０に向けて分流させ、また、潤滑油をオイルパンから給
油路７を経て油冷室９に圧送し、副燃焼室８を冷却して
から放熱器２０を経て放熱させ、再びオイルパンへ還流
させるように構成されている。Embodiments of the present invention will now be described in more detail with reference to the drawings. 1 is a cross-sectional plan view of a main part of a diesel engine showing a first embodiment according to the invention of claim 1, FIG.
FIG. 2 is a vertical sectional view taken along the line I-I of FIG. This engine E
Is constructed as a partially oil-cooled forced air-cooled overhead valve diesel engine as in the prior art. That is, the engine E includes a flywheel fan 21 and a fan case 22 provided on the front side of the engine body 1 and a cylinder head 2
An oil cooler (radiator) 20 provided on the upper front side of the cylinder and a tunnel type cooling air passage 3 formed through the cylinder head 2.
And the oil cooling chamber 9, and comprises a flywheel fan 2
The cooling air A generated in 1 is guided by the fan case 22, and the cylinder block, the tunnel type cooling air passage 3 and the radiator 2 are guided.
In addition, the lubricating oil is diverted toward 0, and the lubricating oil is pressure-fed from the oil pan to the oil cooling chamber 9 via the oil supply path 7 to cool the auxiliary combustion chamber 8 and then to radiate heat via the radiator 20, and then to return to the oil pan again. Is configured to let.
【００１１】本発明の特徴をなすＥＧＲ装置１０は、図
１及び図２に示すように、吸気ポート４の吸気弁口４ａ
と排気ポート５の排気弁口５ａとの間の弁口間肉壁６に
ＥＧＲ制御弁１２を有する排ガス還流通路１１を貫通形
成し、この排ガス還流通路１１で吸気弁口４ａと排気弁
口５ａとを連通するように構成されている。上記吸気ポ
ート４は、吸気弁口４ａからシリンダヘッド２の横一側
に導出され、排気ポート５は吸気ポート４と略直交する
ように排気弁口５ａからシリンダヘッド２の後方横一側
に導出されている。上記トンネル式冷却風路３は、吸気
弁口４ａと排気弁口５ａとに隣接する位置でシリンダボ
ア１８の一端部上側に、シリンダヘッド２を前後方向へ
貫通して形成され、また、副燃焼室８は、上記トンネル
式冷却風路３とは反対側の位置で、シリンダボア１８の
他端部上側に形成されている。As shown in FIGS. 1 and 2, the EGR device 10 which is a feature of the present invention has an intake valve port 4a of the intake port 4.
The exhaust gas recirculation passage 11 having the EGR control valve 12 is formed through the inter-valve wall 6 between the exhaust port 5a and the exhaust port 5a of the exhaust port 5, and the exhaust valve recirculation passage 11 uses the intake valve port 4a and the exhaust valve port 5a. Is configured to communicate with. The intake port 4 is led out to one lateral side of the cylinder head 2 from the intake valve port 4a, and the exhaust port 5 is led out to one lateral rear side of the cylinder head 2 from the exhaust valve port 5a so as to be substantially orthogonal to the intake port 4. Has been done. The tunnel-type cooling air passage 3 is formed at a position adjacent to the intake valve opening 4a and the exhaust valve opening 5a above one end of the cylinder bore 18 so as to pass through the cylinder head 2 in the front-rear direction, and also to the auxiliary combustion chamber. Reference numeral 8 is a position opposite to the tunnel-type cooling air passage 3 and is formed above the other end of the cylinder bore 18.
【００１２】上記排ガス還流通路１１は、図１及び図２
で示すように、前記弁口間肉壁６に吸気ポート５側より
キリ１９で孔加工して貫通形成される。この排ガス還流
通路１１にはＥＧＲ制御弁１２を構成する弁軸１３がヘ
ッドカバー１８側より垂直に組み込まれている。上記Ｅ
ＧＲ制御弁１２は、排ガス還流通路１１に臨む位置に開
口１４を有する弁軸１３と、この弁軸１３の上部の操作
レバー１５を回動操作するアクチュエータ１６とから成
り、アクチュエータ１６が上記弁軸１３を回動操作する
ことにより、排ガス還流通路１１に臨む開口１４の有効
面積を調量して還流排気ガスの還流率を制御するように
構成されている。なお、上記ＥＧＲ制御弁１２は、必ず
しも開口１４の有効面積を調量するものに限らず、エン
ジンの冷始動時の暖機運転時や高負荷運転時にのみ上記
排ガス還流通路１１を開くものでもよい。また、アクチ
ュエータ１６としては吸気負圧で作動するダイヤフラム
弁、暖温度の検出に基づき電子制御回路を介して作動す
るステッピングモータや電磁弁等を用いることができ
る。The exhaust gas recirculation passage 11 is shown in FIGS.
As shown in FIG. 5, a hole 19 is drilled from the intake port 5 side in the wall wall 6 between the valve openings to form a through hole. In the exhaust gas recirculation passage 11, a valve shaft 13 forming an EGR control valve 12 is vertically installed from the head cover 18 side. E above
The GR control valve 12 is composed of a valve shaft 13 having an opening 14 at a position facing the exhaust gas recirculation passage 11, and an actuator 16 for rotating an operating lever 15 above the valve shaft 13, and the actuator 16 is the valve shaft. By rotating 13 the effective area of the opening 14 facing the exhaust gas recirculation passage 11 is adjusted to control the recirculation rate of the recirculated exhaust gas. The EGR control valve 12 is not limited to one that adjusts the effective area of the opening 14, and may open the exhaust gas recirculation passage 11 only during warm-up operation during cold start of the engine or during high-load operation. . Further, as the actuator 16, it is possible to use a diaphragm valve that operates with intake negative pressure, a stepping motor that operates via an electronic control circuit based on detection of a warm temperature, a solenoid valve, or the like.
【００１３】上記構成により、シリンダヘッド２の外に
従来例のような配管をする必要はなく、部品点数の削減
とコスト低減を図ることができる。また、吸気弁口４ａ
と排気弁口５ａとは排ガス還流通路１１によって最短距
離で連通され、この排ガス還流通路１１を流通する間に
還流排気ガスの温度が大幅に低下することは避けられる
ので、冷始動後のエンジンの暖機運転をさらに促進し、
白煙の発生を効果的に防止することができる。With the above construction, it is not necessary to provide piping outside the cylinder head 2 as in the conventional example, and the number of parts and the cost can be reduced. In addition, the intake valve port 4a
And the exhaust valve opening 5a are communicated with each other by the exhaust gas recirculation passage 11 at the shortest distance, and it is possible to prevent the temperature of the recirculated exhaust gas from significantly lowering while flowing through the exhaust gas recirculation passage 11. Further promote warm-up operation,
It is possible to effectively prevent the generation of white smoke.
【００１４】なお、上記弁口間肉壁６には図２で示すよ
うに、排ガス還流通路１１の下側に潤滑油を油冷室９に
圧送する給油路７が貫通形成されており、エンジンの高
負荷運転時には、上記給油路７を介して吸気ポート４へ
の還流排気ガスを適度に冷却する。これにより、還流排
気ガスの密度が増し、見かけの流量は同じでも多くの排
気ガスを還流できる。従って、排ガス還流通路１１の有
効断面積を小さくできるので、本発明のように弁口間肉
壁６に狭い排ガス還流通路１１を形成した場合でもその
必要断面積を十分に確保でき、排気ガス中のＮＯX の発
生を効果的に防止できる。As shown in FIG. 2, an oil supply passage 7 for pumping lubricating oil to the oil cooling chamber 9 is formed through the lower wall of the exhaust gas recirculation passage 11 in the inter-valve wall 6 through the engine. During the high load operation, the recirculated exhaust gas to the intake port 4 is appropriately cooled via the oil supply passage 7. As a result, the density of the recirculated exhaust gas is increased, and a large amount of exhaust gas can be recirculated even if the apparent flow rate is the same. Therefore, the effective cross-sectional area of the exhaust gas recirculation passage 11 can be made small, so that even when the narrow exhaust gas recirculation passage 11 is formed in the inter-valve wall 6 as in the present invention, the necessary cross-sectional area can be sufficiently ensured and the exhaust gas It is possible to effectively prevent the generation of NO x .
【００１５】図３は請求項１の発明に係る第２の実施例
を示すディーゼルエンジンの要部縦断図、図４は図３中
のII−II線矢視縦断面図である。この実施例では、図３
及び図４に示すように、弁口間肉壁６に向けてシリンダ
ヘッド２の副燃焼室８の反対側より横向きにキリ孔を加
工し、このキリ孔１９ａに前記弁軸１３を組み込んであ
る。弁軸１３の基端部はロータリアクチュエータ１６で
回動制御され、弁軸１３の開口１４が弁口間肉壁６で適
度に塞がれてその有効面積が調量される。その他の点は
図１及び図２と同様に構成されている。なお、図３中の
符号２５はオイルパン、２６は潤滑油の圧送ポンプ、２
７はエンジンの潤滑部、２８はリリーフ弁である。FIG. 3 is a longitudinal sectional view of a main part of a diesel engine showing a second embodiment according to the invention of claim 1, and FIG. 4 is a vertical sectional view taken along the line II-II in FIG. In this example, FIG.
Further, as shown in FIG. 4, a hole is machined laterally from the opposite side of the auxiliary combustion chamber 8 of the cylinder head 2 toward the inter-valve wall 6 and the valve shaft 13 is incorporated into the hole 19a. . The base end portion of the valve shaft 13 is rotationally controlled by the rotary actuator 16, the opening 14 of the valve shaft 13 is appropriately closed by the inter-valve wall 6 and the effective area thereof is measured. The other points are the same as those in FIGS. 1 and 2. In FIG. 3, reference numeral 25 is an oil pan, 26 is a lubricating oil pressure pump, and 2 is a lubricating oil pressure pump.
Reference numeral 7 is a lubricating portion of the engine, and 28 is a relief valve.
【００１６】図５は請求項２の発明に係る実施例を示す
ディーゼルエンジンの要部横断平面図である。この実施
例では、図５に示すように、弁口間肉壁６の中央部が薄
く形成され、この弁口間肉壁６にシリンダヘッド２の頂
部より縦向きにキリ孔１９ａを加工し、このキリ孔１９
ａに前記弁軸１３をヘッドカバー１７側から垂直に組み
込んである。この実施例では、キリ孔１９ａは前後一対
の円弧形状をなし、弁軸１３の開口１４はキリ孔１９ａ
で適度に塞がれて有効面積が調量される。この実施例で
は、弁軸１３の開口１４が排ガス還流通路１１を形成す
る。その他の点は図１及び図２と同様に構成されてい
る。FIG. 5 is a cross-sectional plan view of essential parts of a diesel engine showing an embodiment according to the invention of claim 2. In this embodiment, as shown in FIG. 5, the central portion of the inter-valve wall 6 is thinly formed, and a perforated hole 19a is formed in the wall of the inter-valve wall 6 vertically from the top of the cylinder head 2. This drill hole 19
The valve shaft 13 is vertically installed in the a from the head cover 17 side. In this embodiment, the drill hole 19a has a pair of front and rear circular arc shapes, and the opening 14 of the valve shaft 13 has a drill hole 19a.
The area is appropriately blocked and the effective area is measured. In this embodiment, the opening 14 of the valve shaft 13 forms the exhaust gas recirculation passage 11. The other points are the same as those in FIGS. 1 and 2.
【００１７】図６は請求項３の発明に係る実施例を示す
ディーゼルエンジンの要部横断平面図である。この実施
例では、図６に示すように、弁口間肉壁６を前記トンネ
ル式冷却風路３側へ膨出させ、この膨出肉壁部分６ａに
排ガス還流通路１１を形成する。即ち、吸気弁口４ａと
連通する連通凹入部４５を凹入形成するとともに、トン
ネル式冷却風路３側より斜め横向きにキリ孔１９ａをあ
けて上記連通凹入部４５とキリ孔１９ａと連通し、この
キリ孔１９ａに弁軸１３をヘッドカバー１７側から垂直
に組み込んである。上記キリ孔１９ａの先端部は閉止栓
１９ｂで閉止されている。その他の点は図１及び図２と
同様に構成されている。FIG. 6 is a cross-sectional plan view of essential parts of a diesel engine showing an embodiment according to the invention of claim 3. In this embodiment, as shown in FIG. 6, the inter-valve wall 6 is bulged toward the tunnel-type cooling air passage 3 side, and the exhaust gas recirculation passage 11 is formed in the bulged wall portion 6a. That is, the communication recessed portion 45 that communicates with the intake valve port 4a is formed in a recessed shape, and the drilled hole 19a is formed obliquely and laterally from the tunnel type cooling air passage 3 side to communicate with the communication recessed portion 45 and the drilled hole 19a. The valve shaft 13 is vertically installed in the drill hole 19a from the head cover 17 side. The tip of the drill hole 19a is closed by a closing plug 19b. The other points are the same as those in FIGS. 1 and 2.
【００１８】なお、請求項３の発明は、上記膨出肉壁部
分６ａに排ガス還流通路１１を形成するものであれば上
記実施例に限らない。例えば、上記連通凹入部４５とキ
リ孔１９ａとを逆の配置にしたもの、排ガス還流通路１
１が二組の連通凹入部４５を連通して成るもの、二組の
キリ孔１９ａを連通して成るもの等、適宜変更を加えて
実施し得る。また、本発明はディーゼルエンジンに限る
ものではなく、ガソリンエンジンについても、適宜変更
を加えて実施し得ることは、多言を要しない。The invention of claim 3 is not limited to the above embodiment as long as the exhaust gas recirculation passage 11 is formed in the bulged wall portion 6a. For example, the communication recessed portion 45 and the drill hole 19a are arranged in reverse, the exhaust gas recirculation passage 1
1 may be made by connecting two sets of communicating recessed portions 45, two sets may be made by connecting two sets of perforation holes 19a, and the like, and appropriate modifications may be made. Further, the present invention is not limited to a diesel engine, and it is not necessary to say that a gasoline engine can be implemented with appropriate modifications.
【図１】請求項１の発明に係る第１の実施例を示すディ
ーゼルエンジンの要部横断平面図である。FIG. 1 is a cross-sectional plan view of main parts of a diesel engine showing a first embodiment according to the invention of claim 1. FIG.
【図２】図１中のＩ−Ｉ線矢視縦断面図である。FIG. 2 is a vertical cross-sectional view taken along the line II of FIG.
【図３】請求項１の発明に係る第２の実施例を示すディ
ーゼルエンジンの要部縦断図である。FIG. 3 is a longitudinal sectional view of a main part of a diesel engine showing a second embodiment according to the invention of claim 1.
【図４】図３中のII−II線矢視縦断面図である。FIG. 4 is a vertical sectional view taken along the line II-II in FIG.
【図５】請求項２の発明に係るディーゼルエンジンの要
部横断平面図である。FIG. 5 is a cross-sectional plan view of essential parts of the diesel engine according to the invention of claim 2.
【図６】請求項３の発明に係るディーゼルエンジンの要
部横断平面図である。FIG. 6 is a cross-sectional plan view of essential parts of the diesel engine according to the invention of claim 3;
【図７】従来例に係るディーゼルエンジンの要部横断平
面図である。FIG. 7 is a cross-sectional plan view of a main part of a diesel engine according to a conventional example.
Ｅ…エンジン、 ２…シリンダヘッド、 ３…
トンネル式冷却風路、４…吸気ポート、 ４ａ…吸
気弁口、 ５…排気ポート、５ａ…排気弁口、
６…弁口間肉壁、 ６ａ…膨出肉壁部分、１
１…排ガス還流通路、 １２…ＥＧＲ制御弁、 １３
…弁軸、１４…開口、 １９ａ…キリ孔。E ... Engine, 2 ... Cylinder head, 3 ...
Tunnel type cooling air passage, 4 ... intake port, 4a ... intake valve port, 5 ... exhaust port, 5a ... exhaust valve port,
6 ... Meat wall between valve openings, 6a ... Bulging wall part, 1
1 ... Exhaust gas recirculation passage, 12 ... EGR control valve, 13
... valve shaft, 14 ... opening, 19a ... drill hole.
Claims (3)
ート(５)とをＥＧＲ制御弁(12)を有する排ガス還流通路
(11)で連通して構成したエンジンの排ガス再循環装置に
おいて、 上記吸気ポート(４)は、吸気弁口(4a)からシリンダヘッ
ド(２)の横一側に導出し、排気ポート(５)は吸気ポート
(４)と略直交するように排気弁口(5a)からシリンダヘッ
ド(２)の後方横一側に導出し、 上記吸気弁口(4a)と排気弁口(5a)との間の弁口間肉壁
(６)に上記排ガス還流通路(11)を貫通形成して吸気弁口
(4a)と排気弁口(5a)とを上記排ガス還流通路(11)で連通
し、この排ガス還流通路(11)にＥＧＲ制御弁(12)を構成
する弁軸(13)を装着して構成したことを特徴とするエン
ジンの排ガス再循環装置。1. An exhaust gas recirculation passage having an EGR control valve (12) for an intake port (4) and an exhaust port (5) of an engine (E).
In the exhaust gas recirculation system for an engine configured to communicate with each other through (11), the intake port (4) is led out from the intake valve port (4a) to one side of the cylinder head (2), and the exhaust port (5) Is the intake port
(4) Derived from the exhaust valve port (5a) to one rear side of the cylinder head (2) so as to be substantially orthogonal to (4), and the valve port between the intake valve port (4a) and the exhaust valve port (5a). Meat wall
The exhaust gas recirculation passage (11) is formed through (6) to form an intake valve opening.
(4a) and the exhaust valve port (5a) are communicated with each other through the exhaust gas recirculation passage (11), and the exhaust gas recirculation passage (11) is equipped with a valve shaft (13) constituting an EGR control valve (12). Exhaust gas recirculation system for engines characterized by
ート(５)とをＥＧＲ制御弁(12)を有する排ガス還流通路
(11)で連通して構成したエンジンの排ガス再循環装置に
おいて、 上記吸気ポート(４)の吸気弁口(4a)と排気ポート(５)の
排気弁口(5a)との間の弁口間肉壁(６)にシリンダヘッド
(２)の頂部側よりキリ孔(19a)をあけ、このキリ孔(19a)
にＥＧＲ制御弁(12)を構成する弁軸(13)を装着し、この
弁軸(13)に開口(14)をあけて上記排ガス還流通路(11)を
形成し、上記吸気弁口(4a)と排気弁口(5a)とを上記排ガ
ス還流通路(11)で連通して構成したことを特徴とするエ
ンジンの排ガス再循環装置。2. An exhaust gas recirculation passage having an EGR control valve (12) for an intake port (4) and an exhaust port (5) of an engine (E).
In the exhaust gas recirculation device for an engine configured to communicate with each other at (11), between the valve ports between the intake valve port (4a) of the intake port (4) and the exhaust valve port (5a) of the exhaust port (5). Cylinder head on meat wall (6)
Drill a hole (19a) from the top side of (2).
Is equipped with a valve shaft (13) constituting an EGR control valve (12), an opening (14) is opened in the valve shaft (13) to form the exhaust gas recirculation passage (11), and the intake valve port (4a ) And the exhaust valve port (5a) are communicated with each other through the exhaust gas recirculation passageway (11).
ート(５)とをＥＧＲ制御弁(12)を有する排ガス還流通路
(11)で連通して構成したエンジンの排ガス再循環装置に
おいて、 上記吸気ポート(４)は、吸気弁口(4a)からシリンダヘッ
ド(２)の横一側に導出し、排気ポート(５)は吸気ポート
(４)と略直交するように排気弁口(5a)からシリンダヘッ
ド(２)の後方横一側に導出し、 上記吸気弁口(4a)と排気弁口(5a)とに隣接させて、シリ
ンダヘッド(２)を前後方向へ貫通するトンネル式冷却風
路(３)を形成し、 上記吸気弁口(4a)と排気弁口(5a)との間の弁口間肉壁
(６)を上記トンネル式冷却風路(３)側へ膨出させ、 上記膨出肉壁部分(6a)に上記排ガス還流通路(11)を形成
して上記吸気弁口(4a)と排気弁口(5a)とを上記排ガス還
流通路(11)で連通し、この排ガス還流通路(11)にＥＧＲ
制御弁(12)を構成する弁軸(13)を装着して構成したこと
を特徴とするエンジンの排ガス再循環装置。3. An exhaust gas recirculation passage having an EGR control valve (12) for an intake port (4) and an exhaust port (5) of an engine (E).
In the exhaust gas recirculation system for an engine configured to communicate with each other through (11), the intake port (4) is led out from the intake valve port (4a) to one side of the cylinder head (2), and the exhaust port (5) Is the intake port
It is led out from the exhaust valve port (5a) to one rear side of the cylinder head (2) so as to be substantially orthogonal to (4), and is adjacent to the intake valve port (4a) and the exhaust valve port (5a). A tunnel-type cooling air passage (3) that penetrates the cylinder head (2) in the front-rear direction is formed, and a wall wall between valve inlets (4a) and exhaust valve outlets (5a) is formed.
(6) is bulged to the side of the tunnel type cooling air passage (3), and the exhaust gas recirculation passage (11) is formed in the bulging wall portion (6a) to form the intake valve port (4a) and the exhaust valve. The exhaust gas recirculation passage (11) communicates with the mouth (5a), and the EGR is connected to the exhaust gas recirculation passage (11).
An exhaust gas recirculation system for an engine, comprising a valve shaft (13) that constitutes a control valve (12).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6043507A JPH07253054A (en) | 1994-03-15 | 1994-03-15 | Exhaust gas recirculation device of engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6043507A JPH07253054A (en) | 1994-03-15 | 1994-03-15 | Exhaust gas recirculation device of engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07253054A true JPH07253054A (en) | 1995-10-03 |
Family
ID=12665652
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6043507A Pending JPH07253054A (en) | 1994-03-15 | 1994-03-15 | Exhaust gas recirculation device of engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07253054A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100476195B1 (en) * | 2001-12-18 | 2005-03-16 | 현대자동차주식회사 | Exhaust gas recirculation system for internal combustion engine |
| JP2010209775A (en) * | 2009-03-10 | 2010-09-24 | Daihatsu Motor Co Ltd | Exhaust gas recirculating device for internal combustion engine |
-
1994
- 1994-03-15 JP JP6043507A patent/JPH07253054A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100476195B1 (en) * | 2001-12-18 | 2005-03-16 | 현대자동차주식회사 | Exhaust gas recirculation system for internal combustion engine |
| JP2010209775A (en) * | 2009-03-10 | 2010-09-24 | Daihatsu Motor Co Ltd | Exhaust gas recirculating device for internal combustion engine |
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