JPH09264201A - Exhaust recirculation controller for engine - Google Patents
Exhaust recirculation controller for engineInfo
- Publication number
- JPH09264201A JPH09264201A JP8076230A JP7623096A JPH09264201A JP H09264201 A JPH09264201 A JP H09264201A JP 8076230 A JP8076230 A JP 8076230A JP 7623096 A JP7623096 A JP 7623096A JP H09264201 A JPH09264201 A JP H09264201A
- Authority
- JP
- Japan
- Prior art keywords
- exhaust
- valve
- engine
- opening
- closing
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0276—Actuation of an additional valve for a special application, e.g. for decompression, exhaust gas recirculation or cylinder scavenging
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
-
- 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
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
-
- 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
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
- F02M26/44—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which a main EGR passage is branched into multiple passages
-
- 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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
-
- 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
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/14—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system
- F02M26/16—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system with EGR valves located at or near the connection to the exhaust system
-
- 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
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、エンジンの排気還
流制御装置に関し、特にターボ過給機を備えたエンジン
の排気還流制御装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine exhaust gas recirculation control device, and more particularly to an engine exhaust gas recirculation control device equipped with a turbocharger.
【0002】[0002]
【従来の技術】従来より、例えば、図4に示すように、
エンジン1の排気系3(排気マニホールド3A)に、該
排気系3とエンジン1の吸気系2(例えば、吸気マニホ
ールド2A)とを連通する排気還流路8を設け、この排
気還流路8に排気還流弁(以下「EGR弁」という。)
7を設けると共に、このEGR弁7を電子制御装置6に
よってエンジン負荷状態等に応じて開弁することによ
り、排ガスの一部をエンジン1の吸気系2に還流して混
合気の燃焼温度を下げ、もって、NOxの発生量を低減
させるようにした排気還流制御装置10が公知である。2. Description of the Related Art Conventionally, for example, as shown in FIG.
The exhaust system 3 (exhaust manifold 3A) of the engine 1 is provided with an exhaust gas recirculation path 8 that connects the exhaust system 3 and the intake system 2 of the engine 1 (for example, the intake manifold 2A) to the exhaust gas recirculation path 8. Valve (hereinafter referred to as "EGR valve")
7 is provided and the EGR valve 7 is opened by the electronic control unit 6 in accordance with the engine load state and the like, whereby a part of the exhaust gas is returned to the intake system 2 of the engine 1 to lower the combustion temperature of the air-fuel mixture. Therefore, the exhaust gas recirculation control device 10 that reduces the amount of NOx generated is known.
【0003】[0003]
【発明が解決しようとする課題】ところで、近年のター
ボ過給機5を備えたエンジン1において、排ガスを吸気
系2に還流させる場合、図4に示すように、ターボ過給
機5及び吸気管2Bに設けられたインタークーラ5Cの
下流に還流させる手法と、図には示さないが、ターボ過
給機5の上流に還流する手法とが考えられる。しかし、
これらの場合、各々以下のような不具合が生じる。By the way, in the engine 1 equipped with the turbocharger 5 of recent years, when the exhaust gas is recirculated to the intake system 2, as shown in FIG. 4, the turbocharger 5 and the intake pipe are shown. A method of returning to the downstream of the intercooler 5C provided in 2B and a method of returning to the upstream of the turbocharger 5, although not shown in the figure, are considered. But,
In these cases, the following problems occur.
【0004】即ち、排ガスをターボ過給機5及びインタ
ークーラ5Cの下流に還流する場合には、図4に示すよ
うに、ターボ過給機5によって加圧された吸気系2に排
ガスを還流させなければならないために、排気系3(排
気管3B)のタービン5Aの上流に絞り3Cを設けて排
ガスの圧力を或る程度高めておく必要があるが、この絞
り3Cによって排気系3の圧力を上昇させると、エンジ
ン1のポンピングロスの上昇を引き起こすことになる。That is, when the exhaust gas is recirculated downstream of the turbocharger 5 and the intercooler 5C, the exhaust gas is recirculated to the intake system 2 pressurized by the turbocharger 5, as shown in FIG. Since it is necessary to provide a throttle 3C upstream of the turbine 5A of the exhaust system 3 (exhaust pipe 3B) to raise the pressure of the exhaust gas to some extent, the pressure of the exhaust system 3 is increased by this throttle 3C. If it is raised, the pumping loss of the engine 1 will be raised.
【0005】又、排ガスをターボ過給機5のコンプレッ
サ5Bの上流に還流する場合(図示省略)には、排ガス
に混入したカーボン等よってターボ過給機5のコンプレ
ッサ5Bやインタークーラ5Cが汚損されることにな
る。本発明は、かかる事情に鑑みてなされたもので、タ
ーボ過給機を備えたエンジンにおいて、ターボ過給機を
汚損することなく、又、エンジンのポンピングロスの上
昇を引き起こすことなく排気還流を行なうことができる
ターボ過給機を備えたエンジンの排気還流制御装置を提
供することを目的とする。When the exhaust gas is recirculated upstream of the compressor 5B of the turbocharger 5 (not shown), the compressor 5B of the turbocharger 5 and the intercooler 5C are contaminated by carbon and the like mixed in the exhaust gas. Will be. The present invention has been made in view of such circumstances, and in an engine including a turbocharger, exhaust gas recirculation is performed without polluting the turbocharger and causing an increase in pumping loss of the engine. An object of the present invention is to provide an exhaust gas recirculation control device for an engine, which is equipped with a turbocharger.
【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、請求項1の発明は、吸気ポートと第1の排気ポート
が設けられたシリンダヘッドと、上記吸気ポートに接続
された吸気通路と、上記第1の排気ポートに接続された
第1の排気通路と、上記吸気ポートを開閉する吸気弁
と、上記第1の排気ポートを開閉する第1の排気弁と、
上記第1の排気通路に配置されたタービン及び上記吸気
通路に配置されたコンプレッサからなるターボ過給機と
を備えたエンジンの排気還流制御装置に、上記シリンダ
ヘッドに設けられた第2の排気ポートと、該第2の排気
ポートを開閉する第2の排気弁と、該第2の排気弁を開
閉する弁開閉手段と、一端が上記第2の排気ポートに接
続され他端が上記コンプレッサの下流側の吸気通路に開
口する第2の排気通路と、エンジン運転状態に応じて上
記弁開閉手段をして上記第2の排気弁の開閉制御を行な
わせしめる制御手段とを具備したものである。In order to achieve the above object, the invention of claim 1 is a cylinder head provided with an intake port and a first exhaust port, and an intake passage connected to the intake port, A first exhaust passage connected to the first exhaust port, an intake valve that opens and closes the intake port, and a first exhaust valve that opens and closes the first exhaust port,
A second exhaust port provided in the cylinder head in an exhaust gas recirculation control device for an engine, which includes a turbocharger including a turbine arranged in the first exhaust passage and a compressor arranged in the intake passage. A second exhaust valve for opening / closing the second exhaust port, a valve opening / closing means for opening / closing the second exhaust valve, one end connected to the second exhaust port and the other end downstream of the compressor. A second exhaust passage opening to the side intake passage, and control means for controlling the opening / closing of the second exhaust valve by performing the valve opening / closing means in accordance with the engine operating state.
【0007】又、請求項2の発明は、上記制御手段が、
エンジン回転数及びエンジン負荷に応じて、上記弁開閉
手段をして上記第2の排気弁の開閉制御を行なわせるも
のである。又、請求項3の発明は、上記弁開閉手段を、
3次元カムを有するカムシャフトと、該カムシャフトを
軸方向に変位させて第2の排気弁を開閉するための実質
的なカム形状を決定する開閉時期調整手段とで構成した
ものである。According to a second aspect of the invention, the control means is
The valve opening / closing means controls opening / closing of the second exhaust valve in accordance with the engine speed and the engine load. According to the invention of claim 3, the valve opening / closing means is
It is composed of a cam shaft having a three-dimensional cam and an opening / closing timing adjusting means for axially displacing the cam shaft to determine a substantial cam shape for opening and closing the second exhaust valve.
【0008】又、請求項4の発明は、上記第2の排気弁
を電磁弁で構成したものである。又、請求項5の発明
は、上記制御手段が、第1の排気弁が開弁している期間
内に、当該第2の排気弁の開弁を行なうようにしたもの
である。According to a fourth aspect of the invention, the second exhaust valve is an electromagnetic valve. Further, in the invention of claim 5, the control means opens the second exhaust valve within a period in which the first exhaust valve is open.
【0009】(作用)請求項1の発明によれば、排気通
路に絞り弁を設けることなく吸気系より高い圧力の排ガ
スを、吸気系のコンプレッサ下流に還流させることがで
きる。(Operation) According to the invention of claim 1, the exhaust gas having a pressure higher than that of the intake system can be recirculated to the downstream side of the compressor of the intake system without providing a throttle valve in the exhaust passage.
【0010】又、請求項2の発明によれば、NOx排出
量が多いエンジン運転状態を選んで、当該エンジン運転
状態に応じた適量の排気還流を行なうことができる。
又、請求項3の発明によれば、排ガスの圧力の脈動を生
じさせる第1の排気弁の開閉に同期させ、所望の圧力の
排ガスを吸気系に還流させるための第2の排気弁の開閉
制御を簡易に行なうことができる。According to the second aspect of the present invention, it is possible to select an engine operating state with a large amount of NOx emissions and perform an appropriate amount of exhaust gas recirculation according to the engine operating state.
Further, according to the invention of claim 3, the second exhaust valve for opening and closing the exhaust gas of a desired pressure is opened and closed in synchronization with the opening and closing of the first exhaust valve which causes the pulsation of the exhaust gas pressure. Control can be performed easily.
【0011】又、請求項4の発明によれば、第2の排気
弁の開閉動作を、第1の排気弁の動作と完全に独立させ
て、自由度が高く且つ精度の良い排気還流が可能にな
る。又、請求項5の発明によれば、排気通路内の排ガス
の圧力が比較的高い状態で、当該第2の排気弁が開弁さ
れ、排気還流される排ガスの圧力を常に吸気系より高く
できる。Further, according to the invention of claim 4, the opening / closing operation of the second exhaust valve is made completely independent of the operation of the first exhaust valve, so that the exhaust gas recirculation having a high degree of freedom and high accuracy is possible. become. Further, according to the invention of claim 5, the second exhaust valve is opened while the pressure of the exhaust gas in the exhaust passage is relatively high, so that the pressure of the exhaust gas recirculated to the exhaust can be always higher than that of the intake system. .
【0012】[0012]
(第1の実施形態)以下、本発明の第1の実施形態につ
いて、添付図面を参照して説明する。尚、この第1の実
施形態は、請求項1から請求項3及び請求項5に対応す
る。図1はエンジン1の排気還流制御装置100を示す
全体構成図、図2はエンジン1のピストン(図示省略)
の変位と第1,第2の吸気弁21,22及び第1,第2
の排気弁31,32の各々のリフト量変化を表すグラフ
である。(First Embodiment) Hereinafter, a first embodiment of the present invention will be described with reference to the accompanying drawings. Note that the first embodiment corresponds to claims 1 to 3 and claim 5. FIG. 1 is an overall configuration diagram showing an exhaust gas recirculation control device 100 of the engine 1, and FIG. 2 is a piston (not shown) of the engine 1.
Displacement and the first and second intake valves 21, 22 and the first and second intake valves
3 is a graph showing changes in the lift amounts of the exhaust valves 31 and 32 of FIG.
【0013】先ず、エンジン1の排気還流制御装置10
0の構成について説明する。エンジン1は、例えば、4
気筒(#1〜#4)のディーゼルエンジンであり、該エ
ンジン1の排気還流制御装置100は、吸気系20、排
気系30、動弁系40、ターボ過給機50及び開弁時期
制御部60を備えている。First, the exhaust gas recirculation control device 10 of the engine 1
The configuration of 0 will be described. The engine 1 is, for example, 4
A cylinder (# 1 to # 4) diesel engine, the exhaust gas recirculation control device 100 of the engine 1 includes an intake system 20, an exhaust system 30, a valve system 40, a turbocharger 50, and a valve opening timing control unit 60. Is equipped with.
【0014】具体的には、吸気系20は、吸気通路を構
成する吸気マニホールド25及び吸気管27よりなり、
この吸気系20においては、エンジン1のシリンダヘッ
ド1Cに各気筒#1〜#4毎に第1の吸気ポート23、
第2の吸気ポート24が設けられ、該第1の吸気ポート
23、第2の吸気ポート24には吸気マニホールド25
の各枝管25a…が各々接続されている。又、上記第1
の吸気ポート23,第2の吸気ポート24には、各気筒
#1〜#4毎に当該各ポート23,24を開閉する第1
の吸気弁21、第2の吸気弁22が各々設けられている
(図1では、気筒#1についてのみ図示している)。Specifically, the intake system 20 comprises an intake manifold 25 and an intake pipe 27 which form an intake passage.
In the intake system 20, the cylinder head 1C of the engine 1 has a first intake port 23 for each of the cylinders # 1 to # 4.
A second intake port 24 is provided, and an intake manifold 25 is provided in the first intake port 23 and the second intake port 24.
Are connected to the respective branch pipes 25a. In addition, the first
The first intake port 23 and the second intake port 24 of the first opening / closing port 23, 24 for each cylinder # 1 to # 4.
Intake valve 21 and second intake valve 22 are provided (in FIG. 1, only cylinder # 1 is shown).
【0015】又、排気系30は、第1の排気通路を構成
する第1の排気マニホールド35及び排気管37並びに
第2の排気通路を構成する第2の排気マニホールド36
よりなり、この排気系30においては、シリンダヘッド
1Cに第1の排気ポート33,第2の排気ポート34が
各気筒#1〜#4毎に設けられている。このうち第1の
排気ポート33には第1の排気マニホールド35の各枝
管35a…が接続され、第2の排気ポート34には、第
2の排気マニホールド36の一端をなす各枝管36a…
が接続されている。又、第2の排気マニホールド36の
他端36bは、上記吸気マニホールド25の接続部25
cにて開口している。そして、第1の排気ポート33,
第2の排気ポート34には、各気筒#1〜#4毎に当該
各ポート33,34を開閉する第1の排気弁31、第2
の排気弁32が各々設けられている。In addition, the exhaust system 30 includes a first exhaust manifold 35 and an exhaust pipe 37 that form a first exhaust passage, and a second exhaust manifold 36 that forms a second exhaust passage.
In the exhaust system 30, the cylinder head 1C is provided with the first exhaust port 33 and the second exhaust port 34 for each of the cylinders # 1 to # 4. Of these, each branch pipe 35a of the first exhaust manifold 35 is connected to the first exhaust port 33, and each branch pipe 36a forming one end of the second exhaust manifold 36 is connected to the second exhaust port 34.
Is connected. The other end 36b of the second exhaust manifold 36 is connected to the connecting portion 25 of the intake manifold 25.
It is opened at c. Then, the first exhaust port 33,
The second exhaust port 34 includes a first exhaust valve 31 for opening and closing the ports 33, 34 for each of the cylinders # 1 to # 4, a second exhaust valve 31,
Exhaust valves 32 are provided respectively.
【0016】又、動弁系40は、第1〜第3の動弁装置
(図1では第3の動弁装置40Cのみ図示)からなり、
第1の動弁装置は、上記第1の吸気弁21及び第2の吸
気弁22の開閉を行なう吸気弁用カムシャフト及びロッ
カアーム(共に図示省略)からなる。又、第2の動弁装
置は、上記第1の排気弁31の開閉を行なう第1の排気
弁用カムシャフト及びロッカアーム(共に図示省略)か
らなる。又、第3の動弁装置40Cは弁開閉手段として
機能するもので、上記第2の排気弁32の開閉を行なう
第2の排気弁用カムシャフト41及びロッカアーム(図
示省略)並びに開閉時期調整手段としての開弁タイミン
グ調整装置(例えば、油圧アクチュエータ)42とによ
って構成される。The valve operating system 40 comprises first to third valve operating devices (only the third valve operating device 40C is shown in FIG. 1).
The first valve operating device includes an intake valve camshaft and a rocker arm (both not shown) for opening and closing the first intake valve 21 and the second intake valve 22. The second valve operating device includes a first exhaust valve camshaft and a rocker arm (both not shown) for opening and closing the first exhaust valve 31. The third valve operating device 40C functions as a valve opening / closing means, and includes a second exhaust valve camshaft 41 and a rocker arm (not shown) for opening / closing the second exhaust valve 32, and opening / closing timing adjusting means. And a valve opening timing adjusting device (for example, a hydraulic actuator) 42.
【0017】ところで、上記第3の動弁装置40Cの第
2の排気弁用カムシャフト41は、3次元カムを有し、
上記開弁タイミング調整装置42が、後述の電子制御装
置(以下、「ECU」という。)61からの信号に基づ
いて、この3次元カムを有する第2の排気弁用カムシャ
フト41を軸方向に変位させて、ロッカアームと3次元
カムの接点を移動させ、もって、第2の排気弁32を開
閉するための実質的なカム形状を決定する。このように
第2の排気弁用カムシャフト41が軸方向に変位される
と、当該第2の排気弁32の開弁開始タイミングは、図
2に示す範囲(可変幅)内で調整される。The second exhaust valve camshaft 41 of the third valve operating device 40C has a three-dimensional cam.
The valve opening timing adjusting device 42 axially moves the second exhaust valve camshaft 41 having this three-dimensional cam on the basis of a signal from an electronic control device (hereinafter referred to as “ECU”) 61 described later. Displacement moves the contact point between the rocker arm and the three-dimensional cam, thus determining the substantial cam shape for opening and closing the second exhaust valve 32. When the second exhaust valve camshaft 41 is axially displaced in this way, the valve opening start timing of the second exhaust valve 32 is adjusted within the range (variable width) shown in FIG.
【0018】一方、上記排気マニホールド35に接続さ
れた排気管37の途中には、ターボ過給機50のタービ
ン51が配置され、上記吸気マニホールド25に接続さ
れた吸気管27の途中には、ターボ過給機50のコンプ
レッサ52が配置されている。又、吸気管27のコンプ
レッサ52の下流には、インタークーラ53が配置され
ている。On the other hand, the turbine 51 of the turbocharger 50 is arranged in the middle of the exhaust pipe 37 connected to the exhaust manifold 35, and the turbo 51 in the middle of the intake pipe 27 connected to the intake manifold 25. The compressor 52 of the supercharger 50 is arranged. An intercooler 53 is arranged downstream of the compressor 52 in the intake pipe 27.
【0019】又、開弁時期制御部60は、ECU61、
このECU61の入力ポート(図示省略)に接続された
エンジン回転数(Ne)センサ62、エンジン負荷とし
てラック位置を検出するラック位置センサ63、その他
のエンジン運転状態を表す各種パラメータを検出する他
のセンサ(例えば、エンジン冷却温度センサ、吸気温度
センサ、酸素濃度センサ等)64からなる。Further, the valve opening timing control unit 60 includes an ECU 61,
An engine speed (Ne) sensor 62 connected to an input port (not shown) of the ECU 61, a rack position sensor 63 for detecting a rack position as an engine load, and other sensors for detecting various other parameters indicating an engine operating state. (For example, an engine cooling temperature sensor, an intake air temperature sensor, an oxygen concentration sensor, etc.) 64.
【0020】このように構成された排気還流制御装置1
00にあっては、ECU61が、エンジン回転数(N
e)とラック位置等に応じてエンジン運転状態を検知
し、このエンジン回転数(Ne)とラック位置等に応じ
てメモリ(図示省略)に記憶されたプログラムを実行し
て、当該エンジン運転状態に最適な排ガスの還流量(以
下「EGRガス量」という。)を決定する。EGRガス
量を決定する手法としては、例えば、ECU61のメモ
リ(図示省略)に記憶されたマップから、エンジン回転
数(Ne)とラック位置とに基づいて第2の排気弁用カ
ムシャフト41のシャフト変位量(EGRガス量を決定
する制御値)の最適値を読み出し、これを他のセンサ6
4からの信号に基づいて補正して最適のEGRガス量を
得る手法がある。Exhaust gas recirculation control device 1 constructed in this way
00, the ECU 61 determines that the engine speed (N
The engine operating state is detected according to e) and the rack position and the like, and the program stored in the memory (not shown) is executed according to the engine speed (Ne) and the rack position and the like to execute the engine operating state. An optimum exhaust gas recirculation amount (hereinafter referred to as "EGR gas amount") is determined. As a method of determining the EGR gas amount, for example, from the map stored in the memory (not shown) of the ECU 61, the shaft of the second exhaust valve camshaft 41 is determined based on the engine speed (Ne) and the rack position. The optimum value of the displacement amount (control value that determines the EGR gas amount) is read out, and this is read by another sensor 6
There is a method of obtaining the optimum amount of EGR gas by making a correction based on the signal from No. 4.
【0021】ECU61は、このように決定した、最適
のEGRガス量を得るためのシャフト変位量を表す信号
を開弁タイミング調整装置42に出力し、これを受けた
開弁タイミング調整装置42は、第2の排気弁用カムシ
ャフト41を当該シャフト変位量に応じて変位させる。
次に、上記ECU61によってその開弁タイミング(特
に開弁開始タイミング)が制御される第2の排気弁32
の具体的な動作について説明する。The ECU 61 outputs a signal representing the shaft displacement amount for obtaining the optimum EGR gas amount thus determined to the valve opening timing adjusting device 42, and the valve opening timing adjusting device 42 receiving the signal outputs the signal. The second exhaust valve cam shaft 41 is displaced according to the shaft displacement amount.
Next, the second exhaust valve 32 whose valve opening timing (particularly the valve opening start timing) is controlled by the ECU 61.
A specific operation will be described.
【0022】この第2の排気弁32は、そのリフト量
が、図2に示すように、第1の排気弁31のリフト量よ
りも小さな一定値に設定され、又、第2の排気弁32が
開弁している期間(図2のt1〜t3時点間又はt2〜t4
時点間;以下「第2の開弁期間」という)が、第1の排
気弁31が開弁している期間(図2のt1〜t4時点間;
以下「第1の開弁期間」という)に対して相対的に変動
するように制御される(可変域)。As shown in FIG. 2, the lift amount of the second exhaust valve 32 is set to a constant value smaller than the lift amount of the first exhaust valve 31, and the second exhaust valve 32 is also set. Is open (between t1 and t3 in FIG. 2 or t2 and t4)
Between time points; hereinafter referred to as "second valve opening period"), the period during which the first exhaust valve 31 is open (between t1 and t4 time points in FIG. 2;
Hereinafter, it is controlled so as to relatively vary with respect to the “first valve opening period” (variable range).
【0023】この場合、第1の開弁期間は、排ガスが高
温、高圧(高エネルギー)のブローダウン時に効率よ
く、当該排気ガスが第1の排気マニホールド35、排気
管37に供給されるように(効率よく排ガスがタービン
51側に送られるように)、特にその開弁タイミングが
設定される。又、第2の開弁期間は、排気行程でピスト
ン(図示省略)が上昇するときに、比較的低温、低圧の
排ガスが、当該排気系より更に圧力が低い吸気系20に
送られるように、第1の排気弁31の開弁タイミングよ
り遅いタイミングで開弁が始まるように設定される。In this case, during the first valve opening period, the exhaust gas is efficiently supplied to the first exhaust manifold 35 and the exhaust pipe 37 when the exhaust gas is blown down at high temperature and high pressure (high energy). (The exhaust gas is efficiently sent to the turbine 51 side), in particular, the valve opening timing thereof is set. Further, during the second valve opening period, when the piston (not shown) rises in the exhaust stroke, the exhaust gas of relatively low temperature and low pressure is sent to the intake system 20 whose pressure is lower than that of the exhaust system. The valve opening is set to start at a timing later than the valve opening timing of the first exhaust valve 31.
【0024】このように、ブローダウン後の排気行程で
第2の排気弁32を開弁させるようにすることで、EG
Rガスを還流する際に、吸気系20より高圧の状態で排
気系30が当該吸気系20につながるようになるので、
従来のように排気系30に絞りを設ける必要がなく、エ
ンジン1のポンピングロスの上昇を防ぐことができる。
ところで、この排気還流制御装置100では、上記第2
の排気弁32によって還流可能な最大EGRガス量が、
排ガスの30パーセント程度得られるように、第2の排
気弁32のリフト量が決定されている。そして、上記第
2の排気弁32の開弁開始タイミングを、図2に示す可
変幅内(t1〜t2時点間)で調整することによって、同
じリフト量で第2の排気弁32が開弁しても、個々の時
点で排ガスの圧力が変動しているため、実際のEGRガ
ス量を異ならせることができる。Thus, by opening the second exhaust valve 32 in the exhaust stroke after blowdown, the EG
When the R gas is recirculated, the exhaust system 30 is connected to the intake system 20 at a higher pressure than the intake system 20,
There is no need to provide a throttle in the exhaust system 30 as in the conventional case, and the pumping loss of the engine 1 can be prevented from increasing.
By the way, in the exhaust gas recirculation control device 100, the second
The maximum amount of EGR gas that can be recirculated by the exhaust valve 32 of
The lift amount of the second exhaust valve 32 is determined so that about 30% of the exhaust gas can be obtained. Then, by adjusting the valve opening start timing of the second exhaust valve 32 within the variable width shown in FIG. 2 (between time points t1 and t2), the second exhaust valve 32 opens with the same lift amount. However, since the pressure of the exhaust gas fluctuates at each time point, the actual EGR gas amount can be made different.
【0025】因みに、第2の排気弁32を早いタイミン
グで開弁すると(図2の破線)エンジン1シリンダ(図
示省略)の筒内圧が比較的高いときに排ガスが当該第2
の排気マニホールド36を介して吸気マニホールド25
側に還流されるのでEGRガス量は多くなる。反対に、
第2の排気弁32を遅いタイミングで開弁すると(図2
の一点鎖線)EGRガス量は少なくなる。By the way, when the second exhaust valve 32 is opened at an early timing (broken line in FIG. 2), when the in-cylinder pressure of the engine 1 cylinder (not shown) is relatively high, the exhaust gas becomes the second exhaust gas.
Through the exhaust manifold 36 of the intake manifold 25
Since the gas is recirculated to the side, the amount of EGR gas increases. Conversely,
If the second exhaust valve 32 is opened at a late timing (see FIG. 2).
(One-dot chain line) EGR gas amount decreases.
【0026】このように第2の排気弁32の開弁開始タ
イミングを調整するだけで、当該第2の排気マニホール
ド36を介して吸気マニホールド25側に還流されるE
GRガス量を調整することができる。而して、第2の排
気弁32の開弁タイミングは、ECU61により、エン
ジン回転数Neとエンジン負荷(ラック位置)等に応じ
て決定されるので、当該エンジン運転状態に応じた最適
のEGRガス量の制御が行われる。In this way, by simply adjusting the valve opening start timing of the second exhaust valve 32, E which is recirculated to the intake manifold 25 side through the second exhaust manifold 36.
The amount of GR gas can be adjusted. Thus, the valve opening timing of the second exhaust valve 32 is determined by the ECU 61 according to the engine speed Ne, the engine load (rack position), etc., and therefore, the optimum EGR gas according to the engine operating state. A quantity control is performed.
【0027】斯かる排気還流制御は、例えば、エンジン
1の吸気管内圧力に応じて作動する負圧応動弁を用いた
公知の排気還流制御に比べても、精度の高いEGRガス
量の制御が可能になる。尚、最大のEGRガス量が、第
1の排気弁31が閉弁したときにエンジン1のシリンダ
(図示省略)内に残留しているガス量にほぼ等しくなる
ことに着目して、第1の排気弁31の開閉期間の設定
(第1の排気弁用カムシャフトのカム形状の設計)によ
って、当該最大のEGRガス量を正確に決定することも
できる。Such exhaust gas recirculation control can control the EGR gas amount with higher accuracy than, for example, known exhaust gas recirculation control using a negative pressure responsive valve that operates according to the pressure in the intake pipe of the engine 1. become. Note that the maximum EGR gas amount becomes substantially equal to the gas amount remaining in the cylinder (not shown) of the engine 1 when the first exhaust valve 31 is closed, and the first The maximum EGR gas amount can also be accurately determined by setting the opening / closing period of the exhaust valve 31 (designing the cam shape of the first exhaust valve camshaft).
【0028】(第2の実施形態)図3は第2の実施形態
の排気還流制御装置200を全体構成図である。尚、こ
の第2の実施形態は、請求項1、請求項2、請求項4及
び請求項5に対応する。尚、この第2の実施形態では、
第2の排気弁を第1〜第4の電磁弁73a〜73dで構
成した点が、上記した第1の実施形態と異なるものであ
り、従って、第1の実施形態と同一の部材には、同一の
符号を付してその詳細な説明は省略する。(Second Embodiment) FIG. 3 is an overall configuration diagram of an exhaust gas recirculation control device 200 of the second embodiment. The second embodiment corresponds to claims 1, 2, 4, and 5. Incidentally, in the second embodiment,
The point that the second exhaust valve is configured by the first to fourth electromagnetic valves 73a to 73d is different from the above-described first embodiment. Therefore, the same members as those in the first embodiment include: The same reference numerals are given and detailed description thereof is omitted.
【0029】排気還流制御装置200は、吸気系20、
排気系30、動弁系40、ターボ過給機50及び電磁弁
制御部70を備えている。このうち排気系30の各気筒
#1〜#4の第2の排気ポート34…には、第2の排気
弁として第1〜第4の電磁弁73a〜73dが設けられ
ている。動弁系40には、上記第1の吸気弁21及び第
2の吸気弁22の開閉を行なう第1の動弁装置(図示省
略)、上記第1の排気弁31の開閉を行なう第2の動弁
装置(図示省略)が設けられている。The exhaust gas recirculation control device 200 includes an intake system 20,
An exhaust system 30, a valve system 40, a turbocharger 50, and a solenoid valve control unit 70 are provided. Of these, the second exhaust ports 34 of the cylinders # 1 to # 4 of the exhaust system 30 are provided with first to fourth electromagnetic valves 73a to 73d as second exhaust valves. The valve operating system 40 includes a first valve operating device (not shown) for opening and closing the first intake valve 21 and the second intake valve 22, and a second valve operating device for opening and closing the first exhaust valve 31. A valve train (not shown) is provided.
【0030】電磁弁制御部70は、ECU71及びEC
U71の入力ポート(図示省略)に接続されたエンジン
回転数(Ne)センサ62、ラック位置センサ63、ク
ランク角センサ72、他のセンサ64によって構成され
ている。この電磁弁制御部70は、第2の排気弁として
設けられた第1〜第4の電磁弁73a〜73dを、図2
に示すように、その開弁動作(特に開弁開始タイミン
グ)を制御する。The solenoid valve control unit 70 includes an ECU 71 and an EC.
It is composed of an engine speed (Ne) sensor 62, a rack position sensor 63, a crank angle sensor 72, and another sensor 64 connected to an input port (not shown) of U71. The solenoid valve control unit 70 controls the first to fourth solenoid valves 73a to 73d provided as the second exhaust valve as shown in FIG.
As shown in, the valve opening operation (particularly the valve opening start timing) is controlled.
【0031】上記電磁弁制御部70を構成するECU7
1は、上記Neセンサ62,ラック位置センサ63,他
のセンサ64からの信号に基づいてエンジン1の運転状
態を検知し、斯く検知したエンジン運転状態に適したE
GRガス量を決定し、この決定したEGRガス量に応じ
て第1〜第4の電磁弁73a〜73dの開弁している期
間(第2の開弁期間)を表す信号を、これら第1〜第4
の電磁弁73a〜73dに出力する。この場合、ECU
71は、クランク角センサ72からの信号に基づいて第
1の排気弁31が開弁している期間(第1の開弁期間)
若しくはエンジン1のピストン変位を検知し、これら検
知した第1の開弁期間若しくはピストン変位に対して相
対的に第2の開弁期間を決定する。ECU 7 constituting the solenoid valve controller 70
1 detects the operating state of the engine 1 based on the signals from the Ne sensor 62, the rack position sensor 63, and the other sensor 64, and E suitable for the detected engine operating state.
The amount of GR gas is determined, and a signal representing the period during which the first to fourth electromagnetic valves 73a to 73d are open (second valve opening period) is determined according to the determined amount of EGR gas. ~ Fourth
To the solenoid valves 73a to 73d. In this case, the ECU
Reference numeral 71 denotes a period in which the first exhaust valve 31 is open based on a signal from the crank angle sensor 72 (first valve opening period).
Alternatively, the piston displacement of the engine 1 is detected, and the first valve opening period or the second valve opening period relative to the detected piston displacement is determined.
【0032】尚、第1〜第4の電磁弁73a〜73dの
リフト量も、第1の実施形態と同様に、図2に示すよう
に、第1の排気弁31のリフト量よりも小さく設定さ
れ、又、第2の開弁期間も、常に第1の開弁期間内(可
変域)とされている。このように第1〜第4の電磁弁7
3a〜73dの開弁タイミングを調整するだけで、当該
第2の排気マニホールド36を介したEGRガス量を調
整することができる。The lift amounts of the first to fourth solenoid valves 73a to 73d are set smaller than the lift amount of the first exhaust valve 31, as shown in FIG. 2, as in the first embodiment. In addition, the second valve opening period is always within the first valve opening period (variable range). In this way, the first to fourth solenoid valves 7
The EGR gas amount through the second exhaust manifold 36 can be adjusted only by adjusting the valve opening timing of 3a to 73d.
【0033】而して、第2の排気弁32の開弁期間は、
ECU71により、エンジン回転数Neとエンジン負荷
(ラック位置)に応じて決定され、当該エンジン運転状
態に応じたEGRガス量の制御が行われる。このように
第2の排気弁を第1〜第4の電磁弁73a〜73dとし
た場合、第1の排気弁31の動作と完全に独立させて開
閉制御できるので、自由度が高く且つ精度の良い排気還
流が可能になる。Thus, the opening period of the second exhaust valve 32 is
The ECU 71 determines the EGR gas amount according to the engine speed Ne and the engine load (rack position), and controls the EGR gas amount according to the engine operating state. In this way, when the second exhaust valve is the first to fourth electromagnetic valves 73a to 73d, since the opening / closing control can be performed completely independently of the operation of the first exhaust valve 31, the degree of freedom is high and the accuracy is high. Good exhaust gas recirculation is possible.
【0034】尚、この第2の実施形態では、第1〜第4
の電磁弁73a〜73dのリフト量を一定にし、開弁開
始タイミングのみを調整しているが、当該リフト量をも
可変制御してもよい。In the second embodiment, the first to the fourth
Although the lift amounts of the electromagnetic valves 73a to 73d are made constant and only the valve opening start timing is adjusted, the lift amounts may also be variably controlled.
【0035】[0035]
【発明の効果】以上説明した請求項1の発明によれば、
排気系に絞り弁を設けることなく吸気系より高い圧力の
排ガスを、吸気系のコンプレッサ下流に還流させること
ができ、ターボ過給機を汚損することなく、しかも、エ
ンジンのポンピングロスの上昇を引き起こすことなく排
気還流を行なうことができる。According to the first aspect of the present invention described above,
Exhaust gas with a higher pressure than that of the intake system can be recirculated to the downstream side of the compressor of the intake system without providing a throttle valve in the exhaust system, which does not pollute the turbocharger and causes an increase in pumping loss of the engine. Exhaust gas recirculation can be performed without using.
【0036】又、請求項2の発明によれば、NOx排出
量が多いエンジン運転状態を選んで、当該エンジン運転
状態に応じた適量の排気還流を行なうことができ、排気
還流制御の効率化が図れる。又、請求項3の発明によれ
ば、排ガスの圧力の変動を生じさせる第1の排気弁の開
閉に同期させた第2の排気弁の開閉制御を、簡易に行な
うことができる。According to the second aspect of the present invention, it is possible to select an engine operating state with a large amount of NOx emissions and perform an appropriate amount of exhaust gas recirculation according to the engine operating state, thereby improving the efficiency of exhaust gas recirculation control. Can be achieved. According to the third aspect of the invention, the opening / closing control of the second exhaust valve synchronized with the opening / closing of the first exhaust valve that causes the fluctuation of the exhaust gas pressure can be easily performed.
【0037】又、請求項4の発明によれば、第2の排気
弁の開閉動作を、第1の排気弁の動作と完全に独立させ
て、自由度が高く且つ精度の良い排気還流が可能にな
る。又、請求項5の発明によれば、排気系の排ガスの圧
力が高い状態で当該第2の排気弁が開弁されるので、排
気還流される排ガスを常に吸気系より高くできる。Further, according to the invention of claim 4, the opening / closing operation of the second exhaust valve is made completely independent of the operation of the first exhaust valve, so that the exhaust gas recirculation having a high degree of freedom and high accuracy is possible. become. Further, according to the invention of claim 5, the second exhaust valve is opened in a state where the pressure of the exhaust gas in the exhaust system is high, so the exhaust gas recirculated in the exhaust gas can be always higher than that in the intake system.
【図1】第1の実施形態の排気還流制御装置100を示
す全体構成図である。FIG. 1 is an overall configuration diagram showing an exhaust gas recirculation control device 100 of a first embodiment.
【図2】エンジン1のピストン変位と第1の排気弁31
及び第2排気弁32の各々のリフト量変化を表すグラフ
である。FIG. 2 is a piston displacement of the engine 1 and a first exhaust valve 31.
5 is a graph showing changes in lift amount of the second exhaust valve 32.
【図3】第2の実施形態の排気還流制御装置200を示
す全体構成図である。FIG. 3 is an overall configuration diagram showing an exhaust gas recirculation control device 200 of a second embodiment.
【図4】従来の排気還流制御装置10を示す全体構成図
である。FIG. 4 is an overall configuration diagram showing a conventional exhaust gas recirculation control device 10.
1 エンジン 1C シリンダヘッド 20 吸気系 21 第1の吸気弁 22 第2の吸気弁 30 排気系 31 第1の排気弁 32 第2の排気弁 35 第1の排気マニホールド(第1の排気通路) 36 第2の排気マニホールド(第2の排気通路) 37 排気管(第1の排気通路) 40 動弁系 40C 第3の動弁装置(弁開閉手段) 41 第2の排気弁用カムシャフト 42 開弁タイミング調整装置(開閉時期調整手段) 50 ターボ過給機 51 タービン 52 コンプレッサ 60 開弁時期制御部 61 電子制御装置(制御手段) 70 電磁弁制御部 71 電子制御装置(制御手段、弁開閉手段) 73a〜73d 第1〜第4の電磁弁(第2の排気弁) 1 Engine 1C Cylinder Head 20 Intake System 21 First Intake Valve 22 Second Intake Valve 30 Exhaust System 31 First Exhaust Valve 32 Second Exhaust Valve 35 First Exhaust Manifold (First Exhaust Passage) 36th 2 exhaust manifold (second exhaust passage) 37 exhaust pipe (first exhaust passage) 40 valve operating system 40C third valve operating device (valve opening / closing means) 41 second exhaust valve camshaft 42 valve opening timing Adjusting device (opening / closing timing adjusting unit) 50 Turbocharger 51 Turbine 52 Compressor 60 Valve opening timing control unit 61 Electronic control unit (control unit) 70 Electromagnetic valve control unit 71 Electronic control unit (control unit, valve opening / closing unit) 73a to 73d 1st-4th solenoid valve (2nd exhaust valve)
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.6 識別記号 庁内整理番号 FI 技術表示箇所 F02D 13/02 F02D 13/02 H 23/00 23/00 J K F02F 1/42 F02F 1/42 K ─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. 6 Identification code Internal reference number FI Technical display location F02D 13/02 F02D 13/02 H 23/00 23/00 JK F02F 1/42 F02F 1/42 K
Claims (5)
れたシリンダヘッドと、上記吸気ポートに接続された吸
気通路と、上記第1の排気ポートに接続された第1の排
気通路と、上記吸気ポートを開閉する吸気弁と、上記第
1の排気ポートを開閉する第1の排気弁と、上記第1の
排気通路に配置されたタービン及び上記吸気通路に配置
されたコンプレッサからなるターボ過給機とを備えたエ
ンジンの排気還流制御装置において、 上記シリンダヘッドに設けられた第2の排気ポートと、 該第2の排気ポートを開閉する第2の排気弁と、 該第2の排気弁を開閉する弁開閉手段と、 一端が上記第2の排気ポートに接続され、他端が上記コ
ンプレッサの下流側の吸気通路に開口する第2の排気通
路と、 エンジン運転状態に応じて、上記弁開閉手段をして上記
第2の排気弁の開閉制御を行なわせしめる制御手段とを
具備したことを特徴とするエンジンの排気還流制御装
置。1. A cylinder head having an intake port and a first exhaust port, an intake passage connected to the intake port, a first exhaust passage connected to the first exhaust port, and A turbocharger including an intake valve that opens and closes an intake port, a first exhaust valve that opens and closes the first exhaust port, a turbine arranged in the first exhaust passage, and a compressor arranged in the intake passage. An exhaust gas recirculation control device for an engine, comprising a second exhaust port provided in the cylinder head, a second exhaust valve for opening and closing the second exhaust port, and a second exhaust valve. A valve opening / closing means for opening / closing, a second exhaust passage having one end connected to the second exhaust port and the other end opening to an intake passage on the downstream side of the compressor, and the valve opening / closing depending on an engine operating state. Means Exhaust gas recirculation control apparatus for an engine, characterized by comprising a control unit which occupies allowed close control of the performed in the second exhaust valve Te.
ンジン負荷に応じて、上記弁開閉手段をして上記第2の
排気弁の開閉制御を行なわせしめることを特徴とする請
求項1に記載のエンジンの排気還流制御装置。2. The control means controls the valve opening / closing means to control the opening / closing of the second exhaust valve according to the engine speed and the engine load. Exhaust gas recirculation control device for engine.
カムシャフトと、該カムシャフトを軸方向に変位させて
第2の排気弁を開閉するための実質的なカム形状を決定
する開閉時期調整手段とからなることを特徴とする請求
項1又は請求項2に記載のエンジンの排気還流制御装
置。3. The valve opening / closing means includes a cam shaft having a three-dimensional cam, and an opening / closing timing that determines a substantial cam shape for opening / closing the second exhaust valve by displacing the cam shaft in the axial direction. The exhaust gas recirculation control device for an engine according to claim 1 or 2, further comprising an adjusting unit.
れていることを特徴とする請求項1又は請求項2に記載
のエンジンの排気還流制御装置。4. The exhaust gas recirculation control device for an engine according to claim 1, wherein the second exhaust valve is a solenoid valve.
ている期間内に、当該第2の排気弁の開弁を行なうこと
を特徴とする請求項1から請求項4の何れかに記載のエ
ンジンの排気還流制御装置。5. The control means according to claim 1, wherein the second exhaust valve is opened within a period in which the first exhaust valve is open. An exhaust gas recirculation control device for an engine according to claim 1.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP07623096A JP3491791B2 (en) | 1996-03-29 | 1996-03-29 | Engine exhaust recirculation control device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP07623096A JP3491791B2 (en) | 1996-03-29 | 1996-03-29 | Engine exhaust recirculation control device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH09264201A true JPH09264201A (en) | 1997-10-07 |
JP3491791B2 JP3491791B2 (en) | 2004-01-26 |
Family
ID=13599374
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP07623096A Expired - Fee Related JP3491791B2 (en) | 1996-03-29 | 1996-03-29 | Engine exhaust recirculation control device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3491791B2 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2001036797A1 (en) * | 1999-11-15 | 2001-05-25 | Fev Motorentechnik Gmbh | Method for operating a piston-type combustion engine, with a controllable turbocharger and a piston-type internal combustion engine for carrying out said method |
JP2003503626A (en) * | 1999-06-30 | 2003-01-28 | サーブ オートモービル アクティエボラーグ | Combustion engine with exhaust gas recirculation |
JP2010065610A (en) * | 2008-09-10 | 2010-03-25 | Mitsubishi Heavy Ind Ltd | Air supply device of engine with egr device and engine having the same |
WO2010149563A1 (en) * | 2009-06-25 | 2010-12-29 | Avl List Gmbh | Method for operating an internal combustion engine |
JP2012052554A (en) * | 2011-12-12 | 2012-03-15 | Mitsubishi Heavy Ind Ltd | Intake device of engine with egr device and engine including the same |
FR2992027A1 (en) * | 2012-06-14 | 2013-12-20 | Peugeot Citroen Automobiles Sa | Method for controlling introduction of fuel into cylinders of super charged four stroke petrol engine of car, involves determining quantity of fuel fed into cylinders, so that exhaust gas richness is equal to one over average time period |
JP2017180360A (en) * | 2016-03-31 | 2017-10-05 | マツダ株式会社 | Control device of engine |
CN108204283A (en) * | 2016-12-16 | 2018-06-26 | 福特环球技术公司 | For the system and method for shunting exhaust steam turbine system |
JP2019015267A (en) * | 2017-07-10 | 2019-01-31 | マツダ株式会社 | Multi-cylinder engine |
DE102013211366B4 (en) | 2012-06-22 | 2022-08-18 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Engine with dedicated EGR exhaust port and independently deactivatable exhaust valves |
-
1996
- 1996-03-29 JP JP07623096A patent/JP3491791B2/en not_active Expired - Fee Related
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003503626A (en) * | 1999-06-30 | 2003-01-28 | サーブ オートモービル アクティエボラーグ | Combustion engine with exhaust gas recirculation |
WO2001036797A1 (en) * | 1999-11-15 | 2001-05-25 | Fev Motorentechnik Gmbh | Method for operating a piston-type combustion engine, with a controllable turbocharger and a piston-type internal combustion engine for carrying out said method |
JP2010065610A (en) * | 2008-09-10 | 2010-03-25 | Mitsubishi Heavy Ind Ltd | Air supply device of engine with egr device and engine having the same |
WO2010149563A1 (en) * | 2009-06-25 | 2010-12-29 | Avl List Gmbh | Method for operating an internal combustion engine |
JP2012052554A (en) * | 2011-12-12 | 2012-03-15 | Mitsubishi Heavy Ind Ltd | Intake device of engine with egr device and engine including the same |
FR2992027A1 (en) * | 2012-06-14 | 2013-12-20 | Peugeot Citroen Automobiles Sa | Method for controlling introduction of fuel into cylinders of super charged four stroke petrol engine of car, involves determining quantity of fuel fed into cylinders, so that exhaust gas richness is equal to one over average time period |
DE102013211366B4 (en) | 2012-06-22 | 2022-08-18 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Engine with dedicated EGR exhaust port and independently deactivatable exhaust valves |
JP2017180360A (en) * | 2016-03-31 | 2017-10-05 | マツダ株式会社 | Control device of engine |
CN108204283A (en) * | 2016-12-16 | 2018-06-26 | 福特环球技术公司 | For the system and method for shunting exhaust steam turbine system |
CN108204283B (en) * | 2016-12-16 | 2022-05-27 | 福特环球技术公司 | System and method for a split exhaust engine system |
JP2019015267A (en) * | 2017-07-10 | 2019-01-31 | マツダ株式会社 | Multi-cylinder engine |
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---|---|
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