JPH09144606A - Fuel and water injection engine - Google Patents
Fuel and water injection engineInfo
- Publication number
- JPH09144606A JPH09144606A JP7337627A JP33762795A JPH09144606A JP H09144606 A JPH09144606 A JP H09144606A JP 7337627 A JP7337627 A JP 7337627A JP 33762795 A JP33762795 A JP 33762795A JP H09144606 A JPH09144606 A JP H09144606A
- Authority
- JP
- Japan
- Prior art keywords
- fuel
- water
- passage
- engine
- exhaust gas
- 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
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M43/00—Fuel-injection apparatus operating simultaneously on two or more fuels, or on a liquid fuel and another liquid, e.g. the other liquid being an anti-knock additive
- F02M43/04—Injectors peculiar thereto
-
- 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
- F02B47/00—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines
- F02B47/02—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines the substances being water or steam
-
- 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
- F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
- F02M25/022—Adding fuel and water emulsion, water or steam
-
- 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
- F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
- F02M25/022—Adding fuel and water emulsion, water or steam
- F02M25/025—Adding water
- F02M25/03—Adding water into the cylinder or the pre-combustion chamber
-
- 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
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、エンジンが予め設
定された負荷以上の領域で運転しているとき、同エンジ
ンの燃焼室内に、軽油等の燃料と水とを噴射するように
した燃料及び水噴射エンジンに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fuel and a fuel for injecting fuel such as light oil and water into a combustion chamber of the engine when the engine is operating in a region above a preset load. It relates to a water injection engine.
【0002】[0002]
【従来の技術】トラック等車両用のディーゼルエンジン
において、排出ガス中の有害成分、特にNOxを低減す
るために、エンジンの燃焼室内に、軽油等燃料と水とを
噴射する方法が有効であることは、一般に良く知られて
おり、例えば実開平4−104156号公報において、
その一例が開示されている。上記実開平4−10415
6号公報に提案されている噴射装置を具えたエンジン
(以下、場合により、既提案のエンジンという)を含む
通常の燃料及び水噴射エンジンでは、縦軸にエンジン負
荷をとり、横軸にエンジン回転数Neをとって示した図
9において斜線を施した中高負荷領域A、例えば45%
負荷以上の運転領域で燃料及び水の噴射が行なわれ、白
抜きの低負荷領域例えば45%負荷未満の運転領域で
は、水噴射を行なうと運転が不安定又は不能となるた
め、燃料のみが噴射される。2. Description of the Related Art In a diesel engine for vehicles such as trucks, a method of injecting fuel such as light oil and water into a combustion chamber of the engine is effective for reducing harmful components in exhaust gas, particularly NO x. This is generally well known, for example, in Japanese Utility Model Laid-Open No. 4-104156,
One example is disclosed. Actual Kaihei 4-10415
In a normal fuel and water injection engine including an engine equipped with an injection device proposed in Japanese Patent No. 6 (hereinafter, referred to as an already proposed engine), the vertical axis indicates the engine load, and the horizontal axis indicates engine rotation. In FIG. 9 showing the number N e , the shaded middle and high load region A, for example, 45%
Fuel and water are injected in the operating region above the load, and in the white low load region, for example, in the operating region below 45% load, water injection makes the operation unstable or impossible, so only fuel is injected. To be done.
【0003】また、上記既提案のエンジンでは、縦軸に
噴射圧力をとり、横軸にクランク角をとって示した図1
0の噴射パターンを示す線図に記載されているように、
最初に、或る一定量、例えば50mm3/stの初期燃
料Ffの噴射が行なわれたのち、エンジンの運転状態に
応じて設定された可変量の水Wが噴射され、続いて後期
燃料Frの噴射が行なわれるように構成されている。In the above proposed engine, the vertical axis represents the injection pressure and the horizontal axis represents the crank angle.
As shown in the diagram showing the injection pattern of 0,
First, a certain amount, for example, 50 mm 3 / st of the initial fuel F f is injected, and then a variable amount of water W set according to the operating state of the engine is injected, and subsequently the latter fuel F f is injected. The injection of r is performed.
【0004】上記既提案のエンジンでは、燃料及び水の
噴射を行なう上記運転領域A内でも、エンジン回転数及
び負荷如何により、特に負荷が低い部分で、最初に噴射
された初期燃料Ffが未だ着火しないか、着火が不十分
な状態のときに、続いて水が噴射されるため、着火遅れ
が大きく、排気ガス中のHCが増大する傾向があり、ま
た、燃料噴射量が、上記初期燃料Frの噴射量、例えば
50mm3/st以下の低中負荷領域Bでは、水噴射が
行なわれず、燃料のみが噴射されて運転されるため、排
出ガス中のNOxを低減することができない不具合があ
る。In the above-mentioned proposed engine, even in the operating region A where fuel and water are injected, the initially injected initial fuel F f is still low in the part where the load is low depending on the engine speed and load. When the fuel does not ignite or is insufficiently ignited, water is subsequently injected, so that the ignition delay is large and the HC in the exhaust gas tends to increase. In the low / medium load region B where the injection amount of F r is, for example, 50 mm 3 / st or less, water injection is not performed and only fuel is injected to operate, so that NO x in the exhaust gas cannot be reduced. There is.
【0005】一方、エンジンの排気ガスの一部を抽出し
て、同エンジンの各気筒の燃焼室に吸気と共に還流させ
ることによって、排出ガス中のNOxを低減し得ること
は良く知られているが、ディーゼルエンジンの場合、中
高負荷運転領域、例えば図9の運転領域A内の比較的高
負荷部分では、NOx低減に十分な量の排気ガス還流を
行なうと、燃料の燃焼が不十分になりスモークが著しく
悪化するので、通常は、排気ガスの還流が行なわれず、
従ってこの運転領域では十分なNOx低減効果が得られ
ない不都合がある。On the other hand, it is well known that NO x in the exhaust gas can be reduced by extracting a part of the exhaust gas of the engine and returning it to the combustion chamber of each cylinder of the engine together with the intake air. However, in the case of a diesel engine, in the medium and high load operating region, for example, in the relatively high load portion in the operating region A of FIG. 9, if exhaust gas recirculation sufficient for NO x reduction is performed, fuel combustion becomes insufficient. Since the smoke becomes significantly worse, the exhaust gas is not normally recirculated,
Therefore, there is a disadvantage that a sufficient NO x reduction effect cannot be obtained in this operating region.
【0006】[0006]
【発明が解決しようとする課題】本発明は、上記事情に
鑑み創案されたもので、エンジンの全運転領域におい
て、HCの増加及びスモークの悪化を伴なうことなく、
排出ガス中のNOxを効果的に低減することができる、
特に車両用ディーゼルエンジンに適用されて好適な燃料
及び水噴射エンジンを提供することを主たる目的とする
ものである。SUMMARY OF THE INVENTION The present invention was devised in view of the above circumstances, and in the entire operating region of the engine, without increasing HC and worsening smoke,
NO x in the exhaust gas can be effectively reduced,
The main object of the present invention is to provide a fuel and water injection engine suitable for use in a diesel engine for vehicles.
【0007】[0007]
【課題を解決するための手段】上記目的を達成するた
め、本発明は、その先端部分に噴孔を具えたノズルボデ
ィ内に摺動自在に嵌装され閉方向に常時弾性的に付勢さ
れた針弁と、上記ノズルボディ内に上記針弁に臨んで形
成された燃料溜と、上記ノズルボディ内に設けられ、そ
の一端が上記燃料溜に連通されると共に、他端が燃料噴
射ポンプに連通された燃料通路と、上記ノズルボディ内
に設けられ、その一端が上記燃料溜より上流側の燃料通
路に連通されると共に、他端が上記針弁の開弁圧より低
い圧力で水を圧送する水供給ポンプに連通された水通路
とを有し、上記燃料噴射ポンプの燃料通路への燃料供給
休止期間中に上記水供給ポンプから水通路を介して燃料
通路に水が供給された後に、同燃料通路に上記燃料噴射
ポンプから燃料が供給されて上記針弁が開くことによ
り、上記噴孔から燃料及び水が噴射されるように構成さ
れた燃料及び水噴射装置、エンジンの排気ガスの一部を
同エンジンの燃焼室に還流させる排気還流通路、同排気
還流通路に介装された可変開度のEGR弁、及び上記エ
ンジンの運転状態に応じて、上記燃料噴射ポンプの燃料
通路への燃料供給量、上記水供給ポンプの水通路への水
供給量、上記EGR弁の開度を夫々制御する制御装置を
具備したことを特徴とする燃料及び水噴射エンジンを提
案するものである。In order to achieve the above object, the present invention is slidably fitted in a nozzle body having a nozzle hole at its tip and is always elastically biased in the closing direction. A needle valve, a fuel reservoir formed in the nozzle body so as to face the needle valve, and provided in the nozzle body, one end of which is connected to the fuel reservoir and the other end of which is connected to the fuel injection pump. A fuel passage communicated with the nozzle body, one end of which communicates with a fuel passage upstream of the fuel reservoir and the other end of which pumps water at a pressure lower than the opening pressure of the needle valve. Having a water passage communicated with the water supply pump, and after water is supplied to the fuel passage from the water supply pump via the water passage during a fuel supply suspension period to the fuel passage of the fuel injection pump, Fuel is supplied from the fuel injection pump to the fuel passage. The fuel and water injector configured to inject fuel and water from the injection hole when the needle valve is opened, and exhaust gas recirculation for recirculating a part of engine exhaust gas to the combustion chamber of the engine. The passage, the variable opening EGR valve interposed in the exhaust gas recirculation passage, and the fuel supply amount to the fuel passage of the fuel injection pump and the water passage of the water supply pump according to the operating state of the engine. The present invention proposes a fuel and water injection engine including a control device for controlling the water supply amount and the opening degree of the EGR valve, respectively.
【0008】本発明において、上記制御装置は、エンジ
ンの負荷が設定負荷を超える運転領域において上記水供
給ポンプを作動させ、燃料 噴射ポンプの燃料供給休止
期間中に、上記水通路に水を供給すると共に、上記エン
ジンの設定負荷より低負荷の運転領域及び設定負荷を超
える運転領域の双方において、上記EGR弁を開動させ
排気ガスの還流を行なうように構成されることが好まし
い。さらに、上記排気ガスをエンジンの吸気通路に導く
排気ガス還流通路内に上記EGR弁が設けられると共
に、同排気ガス還流通路下流の吸気通路に、排気ガスが
導入された吸気の温度を検出する吸気温度センサが設け
られ、上記制御装置は、同吸気温度センサにより検知さ
れた吸気温度が、エンジン負荷に応じて設定された設定
温度に略等しくなるように、上記EGR弁の開度を制御
するように構成されることが望ましい。In the present invention, the control device operates the water supply pump in an operating region where the load of the engine exceeds the set load, and supplies water to the water passage during a fuel supply suspension period of the fuel injection pump. At the same time, it is preferable that the EGR valve is opened and the exhaust gas is recirculated in both the operating region where the load is lower than the set load of the engine and the operating region where the load exceeds the set load. Further, the EGR valve is provided in the exhaust gas recirculation passage that guides the exhaust gas to the intake passage of the engine, and the intake passage for detecting the temperature of the intake air into which the exhaust gas is introduced is provided in the intake passage downstream of the exhaust gas recirculation passage. A temperature sensor is provided, and the control device controls the opening degree of the EGR valve so that the intake air temperature detected by the intake air temperature sensor becomes substantially equal to the set temperature set according to the engine load. It is desirable to be configured to.
【0009】[0009]
【発明の実施の形態】以下本発明の好ましい実施形態を
添付図面について具体的に説明する。先ず、図1に示し
た概略構成図において、符号10は車両用の直接噴射式
ディーゼルエンジンを概念的に示し、同エンジン10
は、シリンダ12内に摺動自在に嵌装され、その頂部に
適宜形状(図示の場合はトロイダル型)の燃焼室キャビ
ティ14を凹設したピストン16を具え、同ピストン1
6はコネクティングロッド18を介してクランク軸(図
示せず)を回転させる。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be specifically described below with reference to the accompanying drawings. First, in the schematic configuration diagram shown in FIG. 1, reference numeral 10 conceptually represents a direct injection diesel engine for a vehicle.
Is equipped with a piston 16 slidably fitted in a cylinder 12 and having a combustion chamber cavity 14 of an appropriate shape (toroidal type in the case shown) recessed in the top thereof.
6 rotates a crankshaft (not shown) via a connecting rod 18.
【0010】各シリンダ12には、夫々1個以上の吸気
弁20及び排気弁22が設けられ、さらに燃料噴射弁2
4が設けられている。吸気弁20は、吸気通路26と上
記シリンダ12との連通を制御し、排気弁22は、排気
通路28とシリンダ12との連通を制御する。上記吸気
通路26と排気通路28との間に排気ガス還流通路30
が設けられ、同排気ガス還流通路30内に、可変開度の
EGR弁32が介装されている。同EGR弁32には、
通常の吸気弁20及び排気弁22と同様なポペット弁、
或いはバターフライ弁等を適宜採用することができる。
上記吸気通路26には、排気ガス還流通路30の接続部
より下流側に吸気温度センサ34が設けられ、同センサ
34は、取入れられた外気と排気ガス還流通路30から
流入した還流排気ガスとが混合した吸気の温度を検知す
る。Each cylinder 12 is provided with at least one intake valve 20 and at least one exhaust valve 22, and further the fuel injection valve 2 is provided.
4 are provided. The intake valve 20 controls communication between the intake passage 26 and the cylinder 12, and the exhaust valve 22 controls communication between the exhaust passage 28 and the cylinder 12. An exhaust gas recirculation passage 30 is provided between the intake passage 26 and the exhaust passage 28.
Is provided, and an EGR valve 32 having a variable opening degree is provided in the exhaust gas recirculation passage 30. The EGR valve 32 has
A poppet valve similar to the normal intake valve 20 and exhaust valve 22,
Alternatively, a butterfly valve or the like can be appropriately adopted.
An intake air temperature sensor 34 is provided in the intake passage 26 on the downstream side of the connecting portion of the exhaust gas recirculation passage 30, and the intake air temperature sensor 34 detects the outside air taken in and the recirculation exhaust gas flowing from the exhaust gas recirculation passage 30. Detects the temperature of mixed intake air.
【0011】また、上記燃料噴射弁24には、通常の燃
料噴射ポンプ36(図示の場合は、列型燃料噴射ポンプ
が示されている)から燃料噴射管を経て高圧燃料が供給
される。同燃料噴射ポンプ36は、燃料タンク40内に
貯溜されフィードポンプ42によって汲上げられ、フィ
ルタ44で濾過された軽油等の燃料を、所望の高圧力に
加圧してエンジン10の各気筒が圧縮行程上死点付近に
あるときに、上記燃料噴射管38を介して燃料噴射弁2
4に供給する。さらに、上記燃料噴射弁24には、水供
給ポンプ46(図示の場合、燃料噴射ポンプ36と同様
構造の列型噴射ポンプが例示されている)から水噴射管
48を経て水が供給される。同水供給ポンプ46は、水
タンク50内に貯溜され、フィードポンプ52によって
汲上げられフィルタ54によって濾過された水を、上記
燃料噴射弁24の開弁圧より低い適宜圧力に加圧して、
後に詳細に説明するタイミング及び吐出量で上記水噴射
管48に圧送する。なおまた、上記EGR弁32は、エ
ンジン10の運転状態を示す種々の信号又は情報、即
ち、エンジンの回転数を検知する回転数センサ56の出
力信号Ne、エンジンの冷却水温を検知する温度センサ
58の出力信号Tw、上記燃料噴射ポンプ36の燃料供
給量を決定するコントロールレバーの位置を検知するこ
とによりエンジン10の負荷を検出するレバー位置セン
サ60の出力信号Lp、及び上記吸気温度センサ34の
出力信号Tiを受容して、EGR弁の開度設定用アクチ
ュエータ62に駆動出力を供与するコントロールユニッ
ト又は制御装置64によって、その開度を制御される。Further, the fuel injection valve 24 is supplied with high-pressure fuel from an ordinary fuel injection pump 36 (in the case shown, a column fuel injection pump is shown) through a fuel injection pipe. The fuel injection pump 36 pressurizes fuel such as light oil, which is stored in a fuel tank 40 and is pumped up by a feed pump 42 and filtered by a filter 44, to a desired high pressure so that each cylinder of the engine 10 undergoes a compression stroke. When the fuel injection valve 2 is in the vicinity of the top dead center through the fuel injection pipe 38,
4 Further, water is supplied to the fuel injection valve 24 from a water supply pump 46 (in the case shown, a row type injection pump having the same structure as the fuel injection pump 36 is illustrated) via a water injection pipe 48. The water supply pump 46 pressurizes the water stored in the water tank 50, pumped by the feed pump 52, and filtered by the filter 54 to an appropriate pressure lower than the valve opening pressure of the fuel injection valve 24,
It is pressure-fed to the water injection pipe 48 at a timing and a discharge amount which will be described in detail later. Furthermore, the EGR valve 32 is provided with various signals or information indicating the operating state of the engine 10, that is, an output signal N e of a rotation speed sensor 56 that detects the rotation speed of the engine, and a temperature sensor that detects the cooling water temperature of the engine. output signal T w of 58, the output signal L p of the lever position sensor 60 for detecting a load of the engine 10 by detecting the position of the control lever for determining the fuel supply amount of the fuel injection pump 36, and the intake air temperature sensor The opening degree of the EGR valve is controlled by a control unit or controller 64 that receives the output signal T i of the control signal 34 and supplies a drive output to the actuator 62 for setting the opening degree of the EGR valve.
【0012】次に、上記燃料噴射弁24は、図2の断面
図及び図3の部分的拡大断面図に示されているように、
エンジンの各気筒のシリンダ12に臨む先端部分に、複
数の噴孔66を有するノズルボディ68と、ディスタン
スピース70と、ノズルホルダ72とを具え、同ノズル
ボディ68及びノズルホルダ72は、中間にディスタン
スピース70を挟んでリテーニングナット74により、
一体的に結合されている。上記ノズルボディ68内に、
上記噴孔66を開閉制御する針弁76が、図の上下方向
に摺動自在に嵌装され、同針弁76を囲撓して燃料溜7
8が形成されている。また、ノズルボディ68内に、一
端が上記燃料溜78に連通する燃料通路80が設けら
れ、同燃料通路80の他端は、ディスタンスピース70
及びノズルホルダ72内の燃料通路80a及び80b、
更に燃料噴射管38、自体公知の定圧弁82を経て燃料
噴射ポンプ36の吐出口に接続されている。さらに、ノ
ズルボディ68内に、一端が上記燃料溜78の上流側に
おける燃料通路80に連通する水通路84が設けられ、
同水通路84の他端は、ディスタンスピース70及びノ
ズルホルダ72内の水通路84a及び84b、及び水噴
射管48を経て水供給ポンプ46の吐出口に接続されて
おり、上記水通路84aの上流端には、ボール弁86と
セットスプリング88とからなる逆止弁90が介装され
ている。Next, the fuel injection valve 24, as shown in the sectional view of FIG. 2 and the partially enlarged sectional view of FIG.
A nozzle body 68 having a plurality of injection holes 66, a distance piece 70, and a nozzle holder 72 are provided at a tip end portion of each cylinder of the engine facing the cylinder 12, and the nozzle body 68 and the nozzle holder 72 are provided at an intermediate distance. With the retaining nut 74 sandwiching the piece 70,
Are united together. In the nozzle body 68,
A needle valve 76 for controlling the opening and closing of the injection hole 66 is slidably fitted in the vertical direction in the figure, and the needle valve 76 is bent and bent to enclose the fuel reservoir 7.
8 are formed. Further, a fuel passage 80 having one end communicating with the fuel reservoir 78 is provided in the nozzle body 68, and the other end of the fuel passage 80 has a distance piece 70.
And the fuel passages 80a and 80b in the nozzle holder 72,
Further, it is connected to the discharge port of the fuel injection pump 36 via a fuel injection pipe 38 and a constant pressure valve 82 known per se. Further, in the nozzle body 68, a water passage 84, one end of which communicates with a fuel passage 80 on the upstream side of the fuel reservoir 78, is provided.
The other end of the water passage 84 is connected to the discharge port of the water supply pump 46 via the water passages 84a and 84b in the distance piece 70 and the nozzle holder 72, and the water injection pipe 48, and upstream of the water passage 84a. A check valve 90 including a ball valve 86 and a set spring 88 is provided at the end.
【0013】また、上記ノズルホルダ72の内部に、針
弁76に対し略同軸的にスプリング室92が設けられ、
同スプリング室92内に、上記針弁76を常時閉方向に
付勢する第1プレッシャスプリング92及び第2プレッ
シャスプリング94が収容されている。上記燃料噴射ポ
ンプ36から高圧燃料が吐出され、燃料噴射弁24の燃
料通路80a,80b及び80を経て燃料溜78に高圧
燃料の圧力が作用したとき、針弁76の段部に作用する
開弁方向の圧力により上記第1プレッシャスプリング9
4が克服されて針弁76がリフトし噴孔66が開くよう
に構成されており、上記開弁圧力は、一例として180
kg/cm2に設定されている。噴孔66からの噴射が
終ったのち、定圧弁82の良く知られている等圧作用に
より、燃料通路80,80a,80b及び燃料噴射管3
8内の圧力は、上記開弁圧180kg/cm2より十分
低い一定圧、例えば60kg/cm2に設定されてい
る。さらに、上記水供給ポンプ46の吐出水圧は、上記
開弁圧180kg/cm2と定圧弁82の設定圧力60
kg/cm2との間の適宜の中間圧力、例えば80〜1
00kg/cm2に設定されている。A spring chamber 92 is provided inside the nozzle holder 72 substantially coaxially with the needle valve 76.
A first pressure spring 92 and a second pressure spring 94 that normally bias the needle valve 76 in the closing direction are housed in the spring chamber 92. When the high-pressure fuel is discharged from the fuel injection pump 36 and the pressure of the high-pressure fuel acts on the fuel reservoir 78 via the fuel passages 80a, 80b and 80 of the fuel injection valve 24, the valve opening that acts on the step portion of the needle valve 76. The first pressure spring 9 by the pressure in the direction.
4 is overcome and the needle valve 76 is lifted to open the injection hole 66. The valve opening pressure is 180 as an example.
It is set to kg / cm 2 . After the injection from the injection hole 66 is completed, the fuel passages 80, 80a, 80b and the fuel injection pipe 3 are driven by the well-known equal pressure action of the constant pressure valve 82.
The pressure in 8 is set to a constant pressure sufficiently lower than the valve opening pressure of 180 kg / cm 2 , for example, 60 kg / cm 2 . Further, the discharge water pressure of the water supply pump 46 is the valve opening pressure 180 kg / cm 2 and the set pressure 60 of the constant pressure valve 82.
appropriate intermediate pressure between kg / cm 2, for example 1:80
It is set to 00 kg / cm 2 .
【0014】上記燃料及び水噴射装置において、エンジ
ン10の負荷が、予め設定された負荷、例えば45%負
荷以上の運転領域、即ち図4の領域Aでは、コントロー
ルユニット又は制御装置64の指令により、燃料噴射弁
24に燃料噴射ポンプ36から高圧燃料が供給されてい
ない供給休止期間中に、水供給ポンプ46から吐出され
た高圧水が、逆止弁90を経て水通路84bに供給され
る。また上記中高負荷運転領域Aの全領域又は後述する
最高負荷付近を除く大部分の領域で、EGR弁開度設定
用のアクチュエータ62に駆動出力が供与されてEGR
弁32が適宜開度で開かれ、エンジン10の排気通路2
8を流れる排気ガスの一部が還流通路30からEGR弁
32を経て吸気通路26に供給され、吸気と共にエンジ
ンのシリンダ12内に供給される。In the above fuel and water injection device, in the operating region where the load of the engine 10 is a preset load, for example, 45% load or more, that is, in the region A of FIG. 4, in accordance with a command from the control unit or the control device 64, The high-pressure water discharged from the water supply pump 46 is supplied to the water passage 84b via the check valve 90 during the supply stop period in which the high-pressure fuel is not supplied to the fuel injection valve 24 from the fuel injection pump 36. In addition, the drive output is provided to the actuator 62 for setting the EGR valve opening degree in the entire area of the medium-high load operation area A or in most areas except the vicinity of the maximum load described later, and the EGR valve opening degree is set.
The valve 32 is opened at an appropriate opening, and the exhaust passage 2 of the engine 10 is opened.
A part of the exhaust gas flowing through 8 is supplied from the recirculation passage 30 to the intake passage 26 via the EGR valve 32, and is supplied into the cylinder 12 of the engine together with the intake air.
【0015】上記中高負荷運転領域Aにおいて、燃料噴
射弁24の水通路84bに高圧の水が供給されると、燃
料噴射ポンプ36の定圧弁82によって設定されている
燃料通路80内の燃料圧力が、上記水の圧力より低いた
めに、図3に良く示されるように、図中に梨地で示され
ている水が、燃料通路80内の燃料を排除して燃料通路
80内に吐出水量分だけ流入する。続いて、燃料噴射ポ
ンプ36から開弁圧を超える高圧燃料が供給されると、
針弁76が開いて、図10に示されているように、噴孔
66から先ず初期燃料Ffが噴射されたのち水Wが噴射
され、続いて後期燃料Frが噴射される。勿論、噴射さ
れる燃料の総量Ff+Frは、エンジン10の運転状態
に応じて設定される。When high-pressure water is supplied to the water passage 84b of the fuel injection valve 24 in the medium / high load operation region A, the fuel pressure in the fuel passage 80 set by the constant pressure valve 82 of the fuel injection pump 36 is increased. Since the pressure of the water is lower than that of the water, as shown in FIG. 3, the water shown in satin in the drawing removes the fuel in the fuel passage 80 and discharges the fuel into the fuel passage 80 by the amount of discharge water. Inflow. Then, when high-pressure fuel exceeding the valve opening pressure is supplied from the fuel injection pump 36,
The needle valve 76 is opened, and as shown in FIG. 10, the initial fuel F f is first injected from the injection hole 66, and then the water W is injected, and subsequently the latter fuel F r is injected. Of course, the total amount of injected fuel F f + F r is set according to the operating state of the engine 10.
【0016】上記のように、運転領域Aにおいて、水噴
射と共に、排気ガスの還流が行なわれることによって、
吸気の温度が高くなり水噴射時における着火遅れの傾向
が改善され、着火性が向上する。特に、従来着火遅れの
傾向が著しかった相対的に低負荷の領域における着火性
が改善されるので、主として水噴射の効果、及び若干の
排気ガス還流の効果によって、排出ガス中のHC増加傾
向を抑制しながら効果的にNOxの低減を達成すること
ができる。一方、図4の低中負荷領域Bでは、コントロ
ールユニット又は制御装置64の駆動出力によりEGR
弁開度設定用のアクチュエータ62が作動してEGR弁
32が開かれ、排気ガスの還流が行なわれると共に、水
供給ポンプ46からの燃料噴射弁24への高圧水の供給
が停止される。従って、運転領域Bでは、排気ガスの還
流によって排出ガス中のNOxの低減が行なわれる。As described above, in the operating region A, the water is injected and the exhaust gas is recirculated, so that
The temperature of intake air becomes high, the tendency of ignition delay at the time of water injection is improved, and the ignitability is improved. In particular, since the ignitability in the relatively low load region where the tendency of ignition delay is remarkable in the past is improved, the increase in HC in the exhaust gas is mainly caused by the effect of water injection and the effect of a slight exhaust gas recirculation. A reduction of NO x can be effectively achieved while suppressing. On the other hand, in the low / medium load region B of FIG. 4, the EGR is performed by the drive output of the control unit or the control device 64.
The actuator 62 for setting the valve opening is operated to open the EGR valve 32, the exhaust gas is recirculated, and the supply of high-pressure water from the water supply pump 46 to the fuel injection valve 24 is stopped. Therefore, in the operating region B, the NO x in the exhaust gas is reduced by the recirculation of the exhaust gas.
【0017】図8は、上記運転領域A及びBにおけるE
GR弁の開度制御マップの一例を示したものである。こ
の例では、図中に線αで示されているように、排気ガス
圧力と吸気圧力との差圧が小さく、従って排気ガスの還
流が本質的に難かしい最低負荷での弁開度を100%と
すると共に、最高負荷での弁開度を0として、中間負荷
での弁開度を直線的に変化させているが、勿論、この特
性線αは、エンジンの種類により、NOxの低減効果
と、排気ガスの還流によって起り勝ちなスモークの悪化
とを、実験的に確かめて較量し、好ましい特性線Gが決
定される。なお、図示されている線αの最高負荷部分が
一部点線で示されているのは、最高負荷及び隣接する高
負荷部分では、吸気中の酸素量に対し燃料量が相対的に
多いため、多くのエンジンでは、スモークが悪化するこ
とが傾向が強く、排気ガスの還流をやめざるを得ない可
能性があることを表現したものである。FIG. 8 shows E in the above operating regions A and B.
It is an example of a GR valve opening control map. In this example, as indicated by a line α in the figure, the valve opening degree at the minimum load at which the recirculation of the exhaust gas is essentially difficult is 100 because the differential pressure between the exhaust gas pressure and the intake pressure is small. %, And the valve opening at the maximum load is set to 0, and the valve opening at the intermediate load is linearly changed. Of course, this characteristic line α depends on the type of engine to reduce NO x . The effect and the exacerbation of smoke that tends to occur due to exhaust gas recirculation are experimentally confirmed and compared to determine a preferable characteristic line G. It should be noted that the maximum load portion of the illustrated line α is partially indicated by a dotted line because the maximum load and the adjacent high load portion have a relatively large fuel amount with respect to the oxygen amount in the intake air, In many engines, smoke tends to worsen and there is a possibility that the exhaust gas recirculation may have to be stopped.
【0018】次に、図7は縦軸に、燃料量に対する噴射
水量の比をとり、横軸にエンジン負荷をとって水噴射量
制御マップの一例を示したものである。図中に線βで示
されているように、負荷45%未満の運転領域では、水
噴射は行なわれず、負荷45%から70%まで直線的に
噴射量が増大し、負荷70%以上では最大噴射量50%
となる。勿論、上記水噴射特性は、エンジンの種類によ
り、排出ガス中のNOxの低減効果、HCの増加及びス
モークの悪化等を総合的に検討して適宜に変更され、修
正される。Next, FIG. 7 shows an example of a water injection amount control map in which the vertical axis represents the ratio of the injection water amount to the fuel amount and the horizontal axis represents the engine load. As shown by the line β in the figure, in the operating region where the load is less than 45%, water injection is not performed, and the injection amount increases linearly from 45% to 70% load, and when the load is 70% or more, the maximum Injection amount 50%
Becomes Of course, the water injection characteristics are appropriately changed and modified depending on the type of engine by comprehensively considering the effect of reducing NO x in exhaust gas, the increase of HC, the deterioration of smoke, and the like.
【0019】図5は、縦軸に排出ガス中のNOx量をと
り、横軸にエンジン負荷をとって、上述した本発明に係
る燃料及び水噴射エンジンのNOx排出特性を調べたも
のである。図中実線で示した線γは、本発明に係るエン
ジンを示し、一点鎖線で示した線γ′は、排気ガスの還
流も水噴射も行なわないベースエンジンのNOx、排出
量を示している。線γで示されているように、設定負荷
45%未満の低中負荷運転領域Bでは、NOxが負荷と
共に次第に増大し、設定負荷45%以上では水噴射と排
気ガス還流とが行なわれるので、NOxは略直線に近い
レベルで変化する。しかし、排気ガス還流も水噴射も行
なわないベースエンジンのNOx量を示す線γ′と対比
することによって、直ちに理解されるように、大巾なN
Ox低減が達成される。なお、設定負荷を超えた運転領
域Aに記載されている点線γ″は、この運転領域で水噴
射が行なわれず、排気ガス還流のみが行なわれた場合の
NOx量を示す。FIG. 5 shows the NO x emission characteristics of the fuel and water injection engine according to the present invention described above, with the vertical axis representing the NO x amount in the exhaust gas and the horizontal axis representing the engine load. is there. The solid line γ in the figure represents the engine according to the present invention, and the dashed line γ'indicates the NO x and emission amount of the base engine that does not recirculate exhaust gas or inject water. . As shown by the line γ, in the low-medium load operating region B where the set load is less than 45%, NO x gradually increases with the load, and when the set load is 45% or more, water injection and exhaust gas recirculation are performed. , NO x changes at a level close to a substantially straight line. However, by comparing it with the line γ'representing the NO x amount of the base engine that does not perform exhaust gas recirculation or water injection, as will be immediately understood, a large N
O x reduction is achieved. The dotted line γ ″ described in the operating region A in which the set load is exceeded indicates the NO x amount when water injection is not performed in this operating region and only exhaust gas recirculation is performed.
【0020】また図6は、縦軸に排煙濃度(スモーク)
をとり、横軸にエンジン負荷をとって、スモーク性能を
調べた線図である。図中、実線で示したσは燃料及び水
噴射エンジンの排煙濃度を示し、一点鎖線で示した線
σ′はベースエンジンの排煙濃度を示す。また図中の点
線σ″は、設定負荷以上の中高負荷運転領域Aで水噴射
を行なわず、排気ガス還流のみを行なった場合の排煙濃
度を示す。図示のとおり、水噴射と排気ガス還流とを同
時に行なうことによって、スモーク性能の悪化を効果的
に防止することができる。Further, in FIG. 6, the vertical axis represents the smoke concentration (smoke).
FIG. 4 is a diagram in which the smoke load is examined by taking the engine load on the horizontal axis. In the figure, σ indicated by the solid line indicates the smoke concentration of the fuel and water injection engine, and line σ ′ indicated by the alternate long and short dash line indicates the smoke concentration of the base engine. The dotted line σ ″ in the figure shows the smoke concentration when water injection is not performed and only exhaust gas recirculation is performed in the medium-high load operation region A above the set load. As shown in the figure, water injection and exhaust gas recirculation By simultaneously performing and, it is possible to effectively prevent the deterioration of the smoke performance.
【0021】上述したように、本発明において、中高負
荷運転領域Aにおいて、排気ガスの還流を行なう主たる
目的は、高温の排気ガスを加えることによって、吸気の
温度を高くし、水噴射による燃料の着火性の悪化を防止
して排出ガス中のHCの増加及びスモークの悪化を効果
的に抑止しながら、NOxを低減することであるので、
水噴射にも拘わらず燃料の着火性を確保し得る吸気温度
を設定温度Toとし、吸気温度センサー34によって検
知された吸気温度Tiと上記設定吸気温度Toとの偏差
をコントロールユニット又は制御装置64内で演算し、
その偏差に応じた駆動出力をアクチュエータ62に与え
てEGR弁32の開度を制御することが、特に外気温度
が低い場合に極めて有利である。上記設定吸気温度To
は、エンジン負荷に応じて変化する温度でもよく、また
上記中高負荷運転領域A内で或る一定の温度例えば40
℃としてもよい。このことは、前記図8のEGR弁開度
線図において、エンジン負荷が設定負荷以下の運転領域
では、負荷に応じて漸減する開度とし(図示の線α)、
中高運転領域では、線αを負荷と 吸気温度とに関連し
た曲線又は直線に修正することを意味する。As described above, in the present invention, the main purpose of the exhaust gas recirculation in the medium and high load operation region A is to increase the temperature of the intake air by adding the high temperature exhaust gas, and It is to reduce NO x while preventing deterioration of ignitability and effectively suppressing increase of HC in exhaust gas and deterioration of smoke.
The intake air temperature which can ensure the ignitability of the fuel despite water injection and the set temperature T o, the control unit or control the deviation between the sensed intake air temperature T i and the set air temperature T o by the intake air temperature sensor 34 Calculated in the device 64,
It is extremely advantageous to control the opening degree of the EGR valve 32 by giving a drive output according to the deviation to the actuator 62, especially when the outside air temperature is low. The set intake air temperature T o
May be a temperature that changes according to the engine load, and may be a certain constant temperature within the medium-high load operating region A, for example, 40
It is good also as ° C. In the EGR valve opening diagram of FIG. 8, this is the opening that gradually decreases according to the load in the operating region where the engine load is equal to or lower than the set load (line α in the figure),
In the medium to high operating range, it means that the line α is modified to a curve or a straight line related to the load and the intake air temperature.
【0022】なお、エンジンの冷却水温Twを温度セン
サ58により検知し、冷却水温Twが設定温度例えば6
0℃以下の冷態始動時等では、コントロールユニット又
は制御装置64によりアクチュエータ62にEGR弁3
2を全閉させる駆動出力が供給され、排気ガスの還流は
行なわれない。The engine cooling water temperature T w is detected by the temperature sensor 58, and the cooling water temperature T w is set to, for example, 6
At the time of cold start at 0 ° C. or less, the control unit or the control device 64 causes the actuator 62 to move the EGR valve 3
A drive output for fully closing 2 is supplied, and exhaust gas is not recirculated.
【0023】[0023]
【発明の効果】叙上のように、本発明に係る燃料及び水
噴射装置は、その先端部分に噴孔を具えたノズルボディ
内に摺動自在に嵌装され閉方向に常時弾性的に付勢され
た針弁と、上記ノズルボディ内に上記針弁に臨んで形成
された燃料溜と、上記ノズルボディ内に設けられ、その
一端が上記燃料溜に連通されると共に、他端が燃料噴射
ポンプに連通された燃料通路と、上記ノズルボディ内に
設けられ、その一端が上記燃料溜より上流側の燃料通路
に連通されると共に、他端が上記針弁の開弁圧より低い
圧力で水を圧送する水供給ポンプに連通された水通路と
を有し、上記燃料噴射ポンプの燃料通路への燃料供給休
止期間中に上記水供給ポンプから水通路を介して燃料通
路に水が供給された後に、同燃料通路に上記燃料噴射ポ
ンプから燃料が供給されて上記針弁が開くことにより、
上記噴孔から燃料及び水が噴射されるように構成された
燃料及び水噴射装置、エンジンの排気ガスの一部を同エ
ンジンの燃焼室に還流させる排気還流通路、同排気還流
通路に介装された可変開度のEGR弁、及び上記エンジ
ンの運転状態に応じて、上記燃料噴射ポンプの燃料通路
への燃料供給量、上記水供給ポンプの水通路への水供給
量、上記EGR弁の開度を夫々制御する制御装置を具備
してなることを特徴とし、排出ガス中のHC及びスモー
ク増加の不具合を伴なうことなく、従前の同種エンジン
よりNOxを一層低減し得る利点がある。As described above, the fuel and water injection device according to the present invention is slidably fitted in a nozzle body having an injection hole at its tip and is always elastically attached in the closing direction. A biased needle valve, a fuel reservoir formed in the nozzle body facing the needle valve, and provided in the nozzle body, one end of which communicates with the fuel reservoir and the other end of which fuel is injected. A fuel passage communicated with a pump and provided in the nozzle body, one end of which communicates with a fuel passage upstream of the fuel reservoir, and the other end of which has a water pressure lower than the valve opening pressure of the needle valve. And a water passage communicating with a water supply pump for pumping water, and water is supplied from the water supply pump to the fuel passage through the water passage during a fuel supply suspension period to the fuel passage of the fuel injection pump. Later, fuel is supplied from the fuel injection pump to the fuel passage. By opening the said needle valve is,
A fuel and water injection device configured to inject fuel and water from the injection holes, an exhaust gas recirculation passage for recirculating a part of engine exhaust gas to a combustion chamber of the engine, and an exhaust gas recirculation passage interposed therein. Variable opening EGR valve, and the fuel supply amount to the fuel passage of the fuel injection pump, the water supply amount to the water passage of the water supply pump, and the opening degree of the EGR valve according to the operating state of the engine. It is characterized in that it is equipped with a control device for controlling each of the above, and has an advantage that NO x can be further reduced as compared with a conventional engine of the same type without causing a problem of increase in HC and smoke in exhaust gas.
【0024】また、上記制御装置は、エンジンの負荷が
設定負荷を超える運転領域において上記水供給ポンプを
作動させ、燃料噴射ポンプの燃料供給休止期間中に、上
記水通路に水を供給すると共に、上記エンジンの設定負
荷より低負荷の運転領域及び設定負荷を超える運転領域
の双方において上記EGR弁を開動させ排気ガスの還流
を行なうように作動することにより、エンジンの全運転
領域において、排出ガス中のNOxを効果的に低減し得
る利点がある。さらに、上記排気ガスをエンジンの吸気
通路に導く排気ガス還流通路内に上記EGR弁が設けら
れると共に、同排気ガス還流通路下流の吸気通路に、排
気ガスが導入された吸気の温度を検出する吸気温度セン
サが設けられ、上記制御装置は、同吸気温度センサによ
り検知された吸気温度が、エンジン負荷に応じて設定さ
れた設定温度に略等しくなるように、上記EGR弁の開
度を制御することにより、特に、着火性が悪化し易い外
気温が低い状態でも、有効に着火性を向上し、排出ガス
中のNOxを効果的に低減し得る利点がある。Further, the control device operates the water supply pump in an operating region where the load of the engine exceeds the set load, supplies water to the water passage during the fuel supply suspension period of the fuel injection pump, and By operating the EGR valve to operate so as to recirculate exhaust gas in both an operating range of a load lower than the set load of the engine and an operating range exceeding the set load of the engine, exhaust gas is exhausted in the entire operating range of the engine. There is an advantage that the NO x can be effectively reduced. Further, the EGR valve is provided in the exhaust gas recirculation passage that guides the exhaust gas to the intake passage of the engine, and the intake passage for detecting the temperature of the intake air into which the exhaust gas is introduced is provided in the intake passage downstream of the exhaust gas recirculation passage. A temperature sensor is provided, and the control device controls the opening degree of the EGR valve so that the intake air temperature detected by the intake air temperature sensor becomes substantially equal to the set temperature set according to the engine load. Therefore, there is an advantage that the ignitability can be effectively improved and NO x in the exhaust gas can be effectively reduced even in a state where the outside air temperature is low in which the ignitability is apt to be deteriorated.
【図1】本発明の好ましい実施形態を示す概略構成図で
ある。FIG. 1 is a schematic configuration diagram showing a preferred embodiment of the present invention.
【図2】図1における燃料及び水噴射装置の要部を断面
で示した詳細構成図である。FIG. 2 is a detailed configuration diagram showing a cross section of a main part of the fuel and water injection device in FIG.
【図3】図2における燃料噴射弁24の先端部分の拡大
断面図である。3 is an enlarged cross-sectional view of a tip portion of a fuel injection valve 24 in FIG.
【図4】本発明における排気ガス還流のみを行なう運転
領域と、水噴射及び排気ガス還流の双方を行なう運転領
域とを示した線図である。FIG. 4 is a diagram showing an operating region in which only exhaust gas recirculation is performed and an operating region in which both water injection and exhaust gas recirculation are performed in the present invention.
【図5】本発明に係るエンジンの負荷とNOx排出量と
の関係を示した線図である。FIG. 5 is a diagram showing the relationship between the engine load and the NO x emission amount according to the present invention.
【図6】本発明に係るエンジンの負荷と排煙濃度との関
係を示した線図である。FIG. 6 is a diagram showing a relationship between engine load and smoke concentration according to the present invention.
【図7】本発明に係るエンジンの負荷と水噴射量との関
係を示した線図である。FIG. 7 is a diagram showing the relationship between the engine load and the water injection amount according to the present invention.
【図8】本発明に係るエンジンの負荷とEGR弁開度と
の関係を示した線図である。FIG. 8 is a diagram showing the relationship between the engine load and the EGR valve opening according to the present invention.
【図9】従前の燃料及び水噴射エンジンの運転領域を示
した線図である。FIG. 9 is a diagram showing an operating region of a conventional fuel and water injection engine.
【図10】燃料及び水噴射エンジンの噴射パターンを示
した線図である。FIG. 10 is a diagram showing an injection pattern of a fuel and water injection engine.
10…エンジン、12…シリンダ、14…燃焼室キャビ
ティ、16…ピストン、20…吸気弁、22…排気弁、
24…燃料噴射弁、26…吸気通路、28…排気通路、
30…排気ガス還流通路、32…EGR弁、34…吸気
温度センサ、36…燃料噴射ポンプ、46…水供給ポン
プ、56…回転数センサ、58…温度センサ、60…コ
ントロールレバー位置センサ、62…EGR弁開度制御
用アクチュエータ、64…コントロールユニット又は制
御装置、66…噴孔、68…ノズルボディ、70…ディ
スタンスピース、72…ノズルホルダ、76…針弁、7
8…燃料溜、80…燃料通路、82…定圧弁、84…水
通路、90…逆止弁、92…スプリング室、94及び9
6…プレッシャスプリング。10 ... Engine, 12 ... Cylinder, 14 ... Combustion chamber cavity, 16 ... Piston, 20 ... Intake valve, 22 ... Exhaust valve,
24 ... Fuel injection valve, 26 ... Intake passage, 28 ... Exhaust passage,
30 ... Exhaust gas recirculation passage, 32 ... EGR valve, 34 ... Intake air temperature sensor, 36 ... Fuel injection pump, 46 ... Water supply pump, 56 ... Rotation speed sensor, 58 ... Temperature sensor, 60 ... Control lever position sensor, 62 ... EGR valve opening control actuator, 64 ... Control unit or control device, 66 ... Injection hole, 68 ... Nozzle body, 70 ... Distance piece, 72 ... Nozzle holder, 76 ... Needle valve, 7
8 ... Fuel reservoir, 80 ... Fuel passage, 82 ... Constant pressure valve, 84 ... Water passage, 90 ... Check valve, 92 ... Spring chamber, 94 and 9
6 ... Pressure spring.
───────────────────────────────────────────────────── 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 F02M 25/07 550 F02M 25/07 550K 550R 43/04 43/04 61/10 61/10 P 25/02 K R ─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. 6 Identification code Internal reference number FI Technical display location F02M 25/07 550 F02M 25/07 550K 550R 43/04 43/04 61/10 61/10 P 25 / 02 KR
Claims (3)
ィ内に摺動自在に嵌装され閉方向に常時弾性的に付勢さ
れた針弁と、上記ノズルボディ内に上記針弁に臨んで形
成された燃料溜と、上記ノズルボディ内に設けられ、そ
の一端が上記燃料溜に連通されると共に、他端が燃料噴
射ポンプに連通された燃料通路と、上記ノズルボディ内
に設けられ、その一端が上記燃料溜より上流側の燃料通
路に連通されると共に、他端が上記針弁の開弁圧より低
い圧力で水を圧送する水供給ポンプに連通された水通路
とを有し、上記燃料噴射ポンプの燃料通路への燃料供給
休止期間中に上記水供給ポンプから水通路を介して燃料
通路に水が供給された後に、同燃料通路に上記燃料噴射
ポンプから燃料が供給されて上記針弁が開くことによ
り、上記噴孔から燃料及び水が噴射されるように構成さ
れた燃料及び水噴射装置、エンジンの排気ガスの一部を
同エンジンの燃焼室に還流させる排気還流通路、同排気
還流通路に介装された可変開度のEGR弁、及び上記エ
ンジンの運転状態に応じて、上記燃料噴射ポンプの燃料
通路への燃料供給量、上記水供給ポンプの水通路への水
供給量、上記EGR弁の開度を夫々制御する制御装置を
具備したことを特徴とする燃料及び水噴射エンジン。1. A needle valve slidably fitted in a nozzle body having a nozzle hole at its tip and constantly elastically biased in a closing direction, and a needle valve facing the needle valve in the nozzle body. And a fuel passage provided in the nozzle body, one end of which is connected to the fuel reservoir and the other end of which is connected to a fuel injection pump, and the fuel passage which is formed in the nozzle body. One end thereof is connected to a fuel passage upstream of the fuel reservoir, and the other end thereof has a water passage communicated with a water supply pump that pumps water at a pressure lower than the valve opening pressure of the needle valve, After the water is supplied from the water supply pump to the fuel passage through the water passage during the fuel supply stop period to the fuel passage of the fuel injection pump, the fuel is supplied from the fuel injection pump to the fuel passage. By opening the needle valve, fuel is injected from the injection hole. And a fuel and water injection device configured to inject water, an exhaust gas recirculation passage for recirculating a part of engine exhaust gas to the combustion chamber of the engine, and a variable opening degree interposed in the exhaust gas recirculation passage. Control for controlling the fuel supply amount to the fuel passage of the fuel injection pump, the water supply amount to the water passage of the water supply pump, and the opening degree of the EGR valve according to the operating state of the EGR valve and the engine A fuel and water injection engine comprising a device.
負荷を超える運転領域において上記水供給ポンプを作動
させ、燃料噴射ポンプの燃料供給休止期間中に、上記水
通路に水を供給すると共に、上記エンジンの設定負荷よ
り低負荷の運転領域及び設定負荷を超える運転領域の双
方において上記EGR弁を開動させ排気ガスの還流を行
なうことを特徴とする請求項1記載の燃料及び水噴射エ
ンジン。2. The control device operates the water supply pump in an operating region where the load of the engine exceeds a set load, supplies water to the water passage during a fuel supply suspension period of the fuel injection pump, and 2. The fuel and water injection engine according to claim 1, wherein the EGR valve is opened to recirculate exhaust gas in both an operating region where the load is lower than the set load of the engine and an operating region where the load exceeds the set load.
く排気ガス還流通路内に上記EGR弁が設けられると共
に、同排気ガス還流通路下流の吸気通路に、排気ガスが
導入された吸気の温度を検出する吸気温度センサが設け
られ、上記制御装置は、同吸気温度センサにより検知さ
れた吸気温度が、エンジン負荷に応じて設定された設定
温度に略等しくなるように、上記EGR弁の開度を制御
することを特徴とする請求項1又は請求項2記載の燃料
及び水噴射エンジン。3. The EGR valve is provided in an exhaust gas recirculation passage that guides the exhaust gas to an intake passage of an engine, and the temperature of intake air into which the exhaust gas is introduced is controlled in an intake passage downstream of the exhaust gas recirculation passage. An intake air temperature sensor for detecting is provided, and the control device controls the opening degree of the EGR valve so that the intake air temperature detected by the intake air temperature sensor becomes substantially equal to the set temperature set according to the engine load. The fuel and water injection engine according to claim 1 or 2, which is controlled.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP33762795A JP3449080B2 (en) | 1995-11-20 | 1995-11-20 | Fuel and water injection engines |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP33762795A JP3449080B2 (en) | 1995-11-20 | 1995-11-20 | Fuel and water injection engines |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH09144606A true JPH09144606A (en) | 1997-06-03 |
JP3449080B2 JP3449080B2 (en) | 2003-09-22 |
Family
ID=18310441
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Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP33762795A Expired - Lifetime JP3449080B2 (en) | 1995-11-20 | 1995-11-20 | Fuel and water injection engines |
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Country | Link |
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JP (1) | JP3449080B2 (en) |
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US6112705A (en) * | 1998-01-21 | 2000-09-05 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Water injection amount control system for fuel and water injection engine |
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