JPH0476260A - Water injection diesel engine - Google Patents
Water injection diesel engineInfo
- Publication number
- JPH0476260A JPH0476260A JP2185407A JP18540790A JPH0476260A JP H0476260 A JPH0476260 A JP H0476260A JP 2185407 A JP2185407 A JP 2185407A JP 18540790 A JP18540790 A JP 18540790A JP H0476260 A JPH0476260 A JP H0476260A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- fuel
- cylinder
- water
- water supply
- 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
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 75
- 238000002347 injection Methods 0.000 title claims abstract description 54
- 239000007924 injection Substances 0.000 title claims abstract description 54
- 239000000446 fuel Substances 0.000 claims abstract description 69
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 238000010586 diagram Methods 0.000 description 6
- 239000007789 gas Substances 0.000 description 6
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 239000000779 smoke Substances 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229910052757 nitrogen Inorganic materials 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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
- 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
Landscapes
- Combined Controls Of Internal Combustion Engines (AREA)
- Fuel-Injection Apparatus (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は水噴射ディーゼルエンジンに関する。[Detailed description of the invention] [Industrial application field] The present invention relates to water injection diesel engines.
ディーゼルエンジンは圧縮比が高いので燃焼温度が高く
従って排ガス中に窒素酸化物(NOX )が多く含まれ
公害上の問題点となっている。該NOXを低減せしめる
手段としては、同一の燃料噴射弁から燃料および水を同
時に噴射できるようにした燃料、水噴射装置をそなえた
ディーゼルエンジンが有効である。Since diesel engines have a high compression ratio, the combustion temperature is high and the exhaust gas contains a large amount of nitrogen oxides (NOX), which poses a pollution problem. As a means for reducing NOx, a diesel engine equipped with a fuel and water injection device that can simultaneously inject fuel and water from the same fuel injection valve is effective.
このような水噴射装置は、例えば第4図の特開昭63−
227951 (特願昭62−59816)公報で開示
されている。「2種燃料エンジンの噴射システム」の構
成及び機能を利用して第3図に示す構成にて実現するこ
とができる。すなわち第3図において、lは燃料タンク
、2は燃料供給ポンプ、3は燃料噴射ポンプ本体、4は
同プランジャ、5は同バレル、6は同吐出弁、7は該吐
出弁6の側路に設けられた逆止調圧弁、8は燃料噴射管
、40は燃料水噴射弁、9は同本体、10は同噴孔、1
1は同針弁、12は同油溜部、14は針弁を押圧するば
ねである。Such a water injection device is, for example, disclosed in Japanese Patent Application Laid-Open No. 1983-1980 shown in FIG.
227951 (Japanese Patent Application No. 62-59816). This can be realized with the configuration shown in FIG. 3 by utilizing the configuration and functions of the "injection system for dual fuel engine." That is, in FIG. 3, l is the fuel tank, 2 is the fuel supply pump, 3 is the fuel injection pump body, 4 is the plunger, 5 is the barrel, 6 is the discharge valve, and 7 is the side passage of the discharge valve 6. A check pressure regulating valve is provided, 8 is a fuel injection pipe, 40 is a fuel water injection valve, 9 is the same main body, 10 is the same injection hole, 1
1 is a needle valve, 12 is an oil reservoir, and 14 is a spring that presses the needle valve.
一方、19は水タンク、18は水供給ポンプ、17は水
供給管、1Gは水供給電磁弁、15は水供給管、13は
水供給逆止弁で水の制御弁側への燃料又は水の逆流を制
限する構成となってる。また、20は水の供給量及び供
給時期を制御するコントロール装置で、エンジンのクラ
ンク角信号およびその他のエンジン作動条件を入力して
、制御弁16に開閉信号を回線23を介して出力する。On the other hand, 19 is a water tank, 18 is a water supply pump, 17 is a water supply pipe, 1G is a water supply solenoid valve, 15 is a water supply pipe, and 13 is a water supply check valve that supplies fuel or water to the water control valve side. It is configured to limit the backflow of. A control device 20 controls the amount and timing of water supply, which inputs an engine crank angle signal and other engine operating conditions, and outputs an opening/closing signal to the control valve 16 via a line 23.
燃料水噴射弁400本体9には燃料通路22が穿設され
ており、燃料噴射管8および燃料水噴射弁油溜部12と
連通させている。また水供給逆止弁13は同じく燃料水
噴射弁40本体に穿孔された水道路30をへて、上記燃
料通路の途中の合流部31に接続されている。A fuel passage 22 is bored in the main body 9 of the fuel water injection valve 400 and communicates with the fuel injection pipe 8 and the fuel water injection valve oil sump 12 . Further, the water supply check valve 13 is connected to a merging portion 31 in the middle of the fuel passage via a waterway 30 similarly bored in the main body of the fuel water injection valve 40.
次に前記従来例の作用について説明する。Next, the operation of the conventional example will be explained.
水タンク19から水供給ポンプ18によって圧送された
水は、供給管17をとおり燃料噴射ポンプ3のプランジ
ャ4が燃料の圧送を行っていない休止期間中に所定の期
間開弁状態に保持された電磁弁16によって、所定量の
水が供給管I5をへて燃料水噴射弁40に送り込まれる
。このとき燃料噴射ポンプ3の逆止弁7の開弁圧PRお
よび水供給逆止弁13の開弁圧P、とする時、針弁11
の開弁圧P。に対して
P、>p、、P、>p。Water pumped from the water tank 19 by the water supply pump 18 passes through the supply pipe 17, and the plunger 4 of the fuel injection pump 3 is kept in an open state for a predetermined period during the idle period when the plunger 4 of the fuel injection pump 3 is not pumping fuel. The valve 16 allows a predetermined amount of water to be fed into the fuel water injection valve 40 through the supply pipe I5. At this time, when the valve opening pressure PR of the check valve 7 of the fuel injection pump 3 and the valve opening pressure P of the water supply check valve 13 are set, the needle valve 11
The valve opening pressure P. For,P,>p,,P,>p.
とすることによって、供給された水は逆止弁13を通り
、水道路30および合流部31を通って燃料iil路2
路内2内入する。By doing so, the supplied water passes through the check valve 13, passes through the waterway 30 and the confluence part 31, and enters the fuel path 2.
Enter the road 2.
この際燃料通路22内の合流部31より上流、即ち燃料
ポンプ3側にある燃料は、燃料噴射ポンプ3の方向に噴
射管8を通り押しもどされ、逆止弁7を押し開いてプラ
ンジャ室に逆流する。その結果、燃料水噴射弁40内に
は燃料通路22内に所定量の水が満たされた状態となる
。At this time, the fuel located upstream of the confluence 31 in the fuel passage 22, that is, on the fuel pump 3 side, is pushed back through the injection pipe 8 in the direction of the fuel injection pump 3, pushes open the check valve 7, and enters the plunger chamber. flow backwards. As a result, the fuel passage 22 in the fuel water injection valve 40 is filled with a predetermined amount of water.
次いで燃料噴射ポンプ3のプランジャ4が燃料の圧送を
開始すると、噴射管8、燃料通路22および油溜部12
内の圧力が上昇し、針弁11の開弁圧20以上に達する
と針弁11が開かれ、燃料、水、燃料が次々と噴射され
る。この際、逆止弁13の作用により水道路30内の水
は、水タンク19側へ押しもどされることはない。以上
のようにして針弁11の開弁により燃料、水噴射弁の噴
孔10から燃料および水が次々と噴射されることになる
。Next, when the plunger 4 of the fuel injection pump 3 starts pumping fuel, the injection pipe 8, the fuel passage 22, and the oil reservoir 12
When the internal pressure increases and reaches the valve opening pressure of the needle valve 11 of 20 or more, the needle valve 11 is opened and fuel, water, and fuel are injected one after another. At this time, the water in the waterway 30 is not pushed back to the water tank 19 side due to the action of the check valve 13. As described above, when the needle valve 11 is opened, fuel and water are injected one after another from the injection hole 10 of the fuel and water injection valve.
その結果エンジンの燃料室での燃焼温度が低下し、燃焼
火炎内でのNOx発生が抑制され、排ガス中のNOXの
低減が得られる。As a result, the combustion temperature in the fuel chamber of the engine is reduced, the generation of NOx in the combustion flame is suppressed, and the amount of NOx in the exhaust gas is reduced.
ところが多気筒のディーゼルエンジンにおいて、この燃
料水噴射装置を適用する場合、エンジンの気筒毎に燃料
噴射の休止期間中に電磁弁16の開閉時間を同一に設定
しても、水供給ラインの形状寸法が気筒毎のわづかの差
により、各気筒の噴射弁40に供給される水の量の相違
が生じ、この為燃料ポンプ3より各気筒に同一量の噴射
が行われるとすると、水量の差だけ気筒毎に噴射される
燃料量が異なることになり、特にエンジンの高負荷域で
は燃料の量が多い気筒だけ燃料過大となり吐煙の増大や
、燃焼室の熱負荷増大による故障が発止する。また、気
筒毎の出力変化により回転変動の増大や振動の増大など
を招くことになる。However, when this fuel water injection device is applied to a multi-cylinder diesel engine, even if the opening and closing times of the solenoid valve 16 are set to be the same during the fuel injection suspension period for each cylinder of the engine, the shape and size of the water supply line Due to a slight difference between cylinders, there will be a difference in the amount of water supplied to the injection valve 40 of each cylinder. Therefore, if the same amount of water is injected from the fuel pump 3 to each cylinder, there will be a difference in the amount of water. This means that the amount of fuel injected into each cylinder will be different, and especially in the high engine load range, the cylinder with a large amount of fuel will have too much fuel, leading to increased smoke and failure due to increased thermal load on the combustion chamber. . Furthermore, changes in output from cylinder to cylinder will lead to increased rotational fluctuations, increased vibrations, and the like.
本発明の目的は前記従来装置の問題点を解消し、各気筒
に対する水供給量が電磁弁116によれば容易に制御で
きることに着目し、前記水供給量を制御することにより
燃料噴射量の気筒毎の差を少なくし、各気筒の出力を均
一した水噴射ディーゼルエンジンを提供するにある。An object of the present invention is to solve the problems of the conventional device and focus on the fact that the amount of water supplied to each cylinder can be easily controlled by the solenoid valve 116. To provide a water-injected diesel engine that reduces the difference between each cylinder and makes the output of each cylinder uniform.
本発明の水噴射ディーゼルエンジンは、燃料および水を
同一の燃料噴射弁から同時に噴射できるように水を水供
給ポンプ、電磁開閉弁および逆止弁を介して燃料水噴射
弁に供給し、かつその水の供給を電磁開閉弁によって、
燃料噴射ポンプによる噴射終了後から次の噴射までの間
に行なうように開閉制御する燃料水噴射装置を有する多
気筒ディーゼルエンジンにおいて、エンジンの気筒ごと
の排気管通路に排気温度を検出する温度センサを設け、
その出力信号を介して全気筒の平均温度に対する各気筒
の温度差を求め、この温度差に応じて水供給の電磁弁開
弁時間を補正して制御する。The water injection diesel engine of the present invention supplies water to the fuel water injection valve via a water supply pump, an electromagnetic on-off valve, and a check valve so that fuel and water can be injected simultaneously from the same fuel injection valve. Water is supplied by an electromagnetic on-off valve.
In a multi-cylinder diesel engine that has a fuel water injection device that controls opening and closing between the end of injection by the fuel injection pump and the next injection, a temperature sensor is installed in the exhaust pipe passage of each cylinder of the engine to detect the exhaust temperature. established,
The temperature difference of each cylinder with respect to the average temperature of all cylinders is determined via the output signal, and the water supply solenoid valve opening time is corrected and controlled according to this temperature difference.
即ち気筒ごとの排気温度の差が最小となるように水供給
量を制御して、各気筒の燃料の噴射量のばらつきを少く
することを特徴としている。That is, the present invention is characterized in that the amount of water supplied is controlled so that the difference in exhaust gas temperature between cylinders is minimized, thereby reducing variations in the amount of fuel injected into each cylinder.
各気筒毎の排気温度T、(i=1〜NUNはシすると、
各気筒ごとの水供給電磁弁の開期間θ。Exhaust temperature T for each cylinder, (where i=1 to NUN,
The open period θ of the water supply solenoid valve for each cylinder.
(i=1〜N)はθ、=θ。十K (Ti−T)となる
。(i=1-N) is θ, =θ. 10K (Ti-T).
ここでθ。はエンジン回転数、出力など作動状態に応じ
てコントロール装置にて与えられる目標の開弁期間、ま
たKは同じく作動状態に応じて与えられる気筒毎の開期
間を補正するための補正係数である。Here θ. is a target valve opening period given by the control device according to operating conditions such as engine speed and output, and K is a correction coefficient for correcting the opening period for each cylinder, which is also given according to operating conditions.
その結果、気筒毎に供給される水の量は多少ばらつきが
多くなる可能性はあるので、それによるNOX発生抑制
効果には気筒毎に多少のばらつきが出るが、気筒毎の燃
料の噴射量のばらつきは少なくできる。As a result, there is a possibility that the amount of water supplied to each cylinder will vary somewhat, so the NOx generation suppression effect will vary slightly from cylinder to cylinder, but the amount of fuel injected for each cylinder will vary. Variations can be reduced.
以下第1〜2図を参照し本発明の一実施例について説明
する。An embodiment of the present invention will be described below with reference to FIGS. 1 and 2.
第1図は実施例の構成図、第2図はコントロール装置1
20の制御フローを示すブロンク図である。Fig. 1 is a configuration diagram of the embodiment, and Fig. 2 is a control device 1.
FIG. 20 is a block diagram showing the control flow of No. 20;
第1〜p図において、200は多気筒エンジン本体、1
03は燃料噴射ポンプ、108は燃料噴射管、140は
燃料水噴射弁で各気筒毎に設けられている6 119は
水タンク、118は水供給ポンプ、117は水供給管、
116は水供給電磁弁で各気筒毎に燃料水噴射弁140
と共に設けられている。120はコントロール装置、1
23は同装置からの信号を各気筒の電磁弁116に伝え
る回線であるが、燃料噴射ポンプ103および燃料水噴
射弁140の内部構造は、201は燃料噴射ポン110
30回転位置信号を検出するカム角検出装置、202は
同信号をコントローラ装置120に伝える回線、203
は気筒毎の排気通路に設けられた温度センサ、204は
同信号をコントローラに伝える回線である。In figures 1 to p, 200 is a multi-cylinder engine main body, 1
03 is a fuel injection pump, 108 is a fuel injection pipe, 140 is a fuel water injection valve provided for each cylinder 6 119 is a water tank, 118 is a water supply pump, 117 is a water supply pipe,
116 is a water supply solenoid valve, and a fuel water injection valve 140 is provided for each cylinder.
is provided with. 120 is a control device, 1
23 is a line that transmits a signal from the same device to the electromagnetic valve 116 of each cylinder, and the internal structure of the fuel injection pump 103 and the fuel water injection valve 140 is
30 A cam angle detection device that detects a rotational position signal, 202 is a line that transmits the signal to the controller device 120, 203
204 is a temperature sensor provided in the exhaust passage of each cylinder, and 204 is a line that transmits the same signal to the controller.
エンジンの回転数、負荷など作動状態に応じて予め設定
されている水供給電磁弁116の開弁期間θ。に応じて
コントローラ装置120から電磁弁116へ開弁信号が
送られ、各気筒の燃料水噴射弁140に水が供給される
と、各気筒毎に水供給量の差に応じて、各気筒毎の排気
温度センサ203からの信号T、(i=i〜N、Nはシ
リンダ数)がコントローラ装置に出力される。The opening period θ of the water supply solenoid valve 116 is preset according to the operating state such as engine speed and load. When a valve opening signal is sent from the controller device 120 to the solenoid valve 116 in accordance with A signal T from the exhaust gas temperature sensor 203 (i=i to N, N is the number of cylinders) is output to the controller device.
そこでコントローラ装置120では、第2図のように排
気温度センサ203からの入力信号を入力信号変換装置
により変換し、平均温度算出部に期間θ。および補正係
数にの設定値は外部からの設定値入力あるいはエンジン
回転数および負荷レバー位置の検出値により設定される
。これらを用いて各気筒毎の補正された開期間θi−θ
。十K(Ti−T)を演算し、その結果に従って出力信
号変換装置より各気筒毎の電磁弁116に開弁信号を送
ることにより、T10気筒毎のばらつきが常時最小とな
るように制御される。Therefore, in the controller device 120, as shown in FIG. 2, the input signal from the exhaust gas temperature sensor 203 is converted by the input signal conversion device, and the average temperature calculation section is converted to the period θ. The set values for the correction coefficients are set by external set value inputs or detected values of the engine rotation speed and load lever position. Using these, the corrected open period θi−θ for each cylinder
. By calculating 10K (Ti-T) and sending a valve opening signal from the output signal conversion device to the solenoid valve 116 of each cylinder according to the result, the variation among the T10 cylinders is controlled to be always minimized. .
なお、電磁弁116の開弁信号の出力は、カム角検出装
置201の信号により回転速度および気筒判別を演算の
うえ、各気筒毎の燃料噴射が休止されている期間中に、
出力されるように設定制御される。Note that the output of the valve opening signal of the solenoid valve 116 is determined by calculating the rotational speed and cylinder discrimination based on the signal of the cam angle detection device 201, and then calculating the output of the valve opening signal of the solenoid valve 116 during the period when fuel injection for each cylinder is suspended.
The setting is controlled so that it is output.
本発明の水噴射ディーゼルエンジンは前記のとおり構成
したので、各気筒毎の排気温度のばらつきに応じて各気
筒への水供給電磁弁の開弁時間を補正して制御すること
により、気筒毎の排気温度のばらつきは最小となり、各
気筒毎の水供給によるNOX発生の抑制効果による多少
のばらつきは生じるが、その結果気筒毎の出力のバラツ
キにより生じる回転変動や振動の増大を回避することが
でき、またエンジンの高負荷域などにおいては、特定気
筒の燃料量のバラツキによる吐煙の増大や燃料室の熱負
荷増大などによる故障を回避することができ、信較性が
高く且低NOXの水噴射ディーゼルエンジンを実現する
ことができる。Since the water injection diesel engine of the present invention is configured as described above, by correcting and controlling the opening time of the water supply solenoid valve to each cylinder according to the variation in exhaust gas temperature for each cylinder, The variation in exhaust temperature is minimized, and although some variation occurs due to the effect of suppressing NOx generation due to the water supply to each cylinder, as a result, it is possible to avoid rotational fluctuations and increases in vibration caused by variations in output between cylinders. In addition, in high engine load ranges, it is possible to avoid failures due to increased smoke emissions due to variations in the amount of fuel in specific cylinders or increased heat load on the fuel chamber, and it is possible to avoid failures due to increased smoke emissions due to variations in the amount of fuel in specific cylinders, increased heat load on the fuel chamber, etc. An injection diesel engine can be realized.
第1〜2図は本発明に係わるもので、第1図は実施例の
構成図、第2図はコントロール装置120の制御フロー
を示すブロック図、第3〜4図は従来例で第3図は水燃
料ディーゼルエンジンの構成を示すブロック図、第4図
は2種燃料ディーゼルエンジンの第3図応当図である。
7・・・逆止調圧弁、13・・・逆止弁、103・・・
燃料噴射ポンプ、116・・・電磁開閉弁、120・・
・コントロール装置、140・・・水燃料噴射弁、20
0・・・エンジン、203・・・排気温度センサ。
120 コントロール装置1 and 2 are related to the present invention; FIG. 1 is a configuration diagram of an embodiment, FIG. 2 is a block diagram showing a control flow of the control device 120, and FIGS. 3 and 4 are conventional examples, and FIG. 4 is a block diagram showing the configuration of a water fuel diesel engine, and FIG. 4 is a diagram corresponding to FIG. 3 of a dual fuel diesel engine. 7... Check pressure regulating valve, 13... Check valve, 103...
Fuel injection pump, 116...Solenoid on-off valve, 120...
・Control device, 140... Water fuel injection valve, 20
0...Engine, 203...Exhaust temperature sensor. 120 Control device
Claims (1)
弁と逆向きの流れのみを許容する逆止調圧弁(7)と、
水供給ポンプで加圧された水をコントロール装置(12
0)を介して適切な送水量と送水タイミングをもって燃
料噴射弁に送水する制御弁(116)と、前記水供給路
(21)内で、燃料噴射弁の油溜部近傍に設けられた水
供給逆止弁(13)とを有してなり、さらに前記逆止調
圧弁、逆止弁、燃料噴射弁の開弁圧をそれぞれP_R、
P_P、P_OとしたときP_R<P_O、P_P<P
_Oとなるように設定したものにおいて;各気筒ごとの
排気温度を検出する温度センサ(203)と;その信号
を用いて全気筒の平均温度に対する各気筒の温度との偏
差に応じ水供給の制御弁(116)の開弁時間を補正し
て制御する制御装置とを有してなる水噴射ディーゼルエ
ンジン。a check pressure regulating valve (7) that is provided in parallel with the discharge valve (6) of the fuel injection pump and allows flow only in the opposite direction to the discharge valve;
A control device (12
a control valve (116) that sends water to the fuel injection valve with an appropriate amount and timing through the water supply channel (21); and a check valve (13), and the valve opening pressure of the check pressure regulating valve, the check valve, and the fuel injection valve is set to P_R, respectively.
When P_P and P_O, P_R<P_O, P_P<P
A temperature sensor (203) that detects the exhaust gas temperature of each cylinder; and a temperature sensor (203) that detects the exhaust gas temperature of each cylinder; and the water supply is controlled according to the deviation of the temperature of each cylinder from the average temperature of all cylinders using the signal. A water injection diesel engine comprising a control device that corrects and controls the opening time of a valve (116).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2185407A JP2675655B2 (en) | 1990-07-16 | 1990-07-16 | Water injection diesel engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2185407A JP2675655B2 (en) | 1990-07-16 | 1990-07-16 | Water injection diesel engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0476260A true JPH0476260A (en) | 1992-03-11 |
JP2675655B2 JP2675655B2 (en) | 1997-11-12 |
Family
ID=16170255
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2185407A Expired - Lifetime JP2675655B2 (en) | 1990-07-16 | 1990-07-16 | Water injection diesel engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2675655B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100440145B1 (en) * | 2001-12-18 | 2004-07-12 | 현대자동차주식회사 | Water injecting system of diesel engine and control method thereof |
-
1990
- 1990-07-16 JP JP2185407A patent/JP2675655B2/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100440145B1 (en) * | 2001-12-18 | 2004-07-12 | 현대자동차주식회사 | Water injecting system of diesel engine and control method thereof |
Also Published As
Publication number | Publication date |
---|---|
JP2675655B2 (en) | 1997-11-12 |
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