JPH09280118A - Egr device for diesel engine - Google Patents
Egr device for diesel engineInfo
- Publication number
- JPH09280118A JPH09280118A JP8094079A JP9407996A JPH09280118A JP H09280118 A JPH09280118 A JP H09280118A JP 8094079 A JP8094079 A JP 8094079A JP 9407996 A JP9407996 A JP 9407996A JP H09280118 A JPH09280118 A JP H09280118A
- Authority
- JP
- Japan
- Prior art keywords
- intake air
- intake
- egr
- cooling device
- heat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- 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
- 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
- F02B29/0412—Multiple heat exchangers arranged in parallel or in series
-
- 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
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/23—Layout, e.g. schematics
- F02M26/27—Layout, e.g. schematics with air-cooled heat exchangers
-
- 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
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
- F02M26/30—Connections of coolers to other devices, e.g. to valves, heaters, compressors or filters; Coolers characterised by their location on the engine
-
- 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】本発明は過給機付ディーゼル
エンジンの吸気空気の温度を下げて空気の吸入効率を向
上させて、エンジンの燃焼を良好に保つと共に、燃焼温
度を下げてＮＯxの排出量を低減するためのインターク
ーラ付ディーゼルエンジン用ＥＧＲ装置に関するもので
ある。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention lowers the temperature of intake air of a diesel engine with a supercharger to improve the intake efficiency of the air to maintain good engine combustion and lowers the combustion temperature to discharge NOx. The present invention relates to an EGR device for a diesel engine with an intercooler for reducing the amount.
【０００２】[0002]
【従来の技術】ディーゼルエンジンの排ガス対策におい
て、排気ガス中のＮＯx の排出量を低減するために、不
活性ガスである排気ガスの一部を吸気に還流すること
で、燃焼温度を低く抑えてＮＯx の生成を抑制させるＥ
ＧＲ（排気再循環）が有効であることが知られ、広く実
用化されている。2. Description of the Related Art As a measure for exhaust gas of a diesel engine, in order to reduce the amount of NOx in the exhaust gas, a part of the exhaust gas which is an inert gas is returned to the intake air to keep the combustion temperature low. E that suppresses the generation of NOx
GR (exhaust gas recirculation) is known to be effective and has been widely put to practical use.
【０００３】このＥＧＲにおいては、排気ガスの再循環
量の割合を増加してＥＧＲ率を高める程、ＮＯx の排出
量を低減できるが、その一方で、シリンダー内に入る吸
気ガス量内の空気量がＥＧＲガスの分だけ減少するた
め、吸気ガス中の空気量が減って燃焼が悪くなるため、
スモークの増加を招く。このスモークの増加を防ぎなが
ら、ＥＧＲガス量を増加するために、ＥＧＲガスを冷却
して体積を減少させて、吸気時のシリンダー内のＥＧＲ
ガスの占める割り合いを少なくして、シリンダー内に入
る空気量を十分に確保する方法が採用されている。In this EGR, the NOx emission amount can be reduced as the EGR rate is increased by increasing the ratio of the exhaust gas recirculation amount, while the air amount in the intake gas amount entering the cylinder is reduced. Is reduced by the amount of EGR gas, the amount of air in the intake gas is reduced, and combustion deteriorates.
It causes an increase in smoke. In order to increase the amount of EGR gas while preventing this increase in smoke, the EGR gas is cooled to reduce its volume, and the EGR in the cylinder during intake is reduced.
A method is adopted in which the proportion of gas is reduced to ensure a sufficient amount of air entering the cylinder.
【０００４】そして、このＥＧＲガスの冷却には、図３
に示すように、排気マニホールド２と吸気管路５を結ぶ
ＥＧＲ管路７に水冷式のＥＧＲクーラ12を設置して、冷
却水Ｗを用いてＥＧＲガスｇを冷却する方法や、図４に
示すように、過給機４のコンプレッサ４ｂと吸気マニホ
ールド３を結ぶ吸気管路５に吸気空気ａの冷却用のイン
タークーラ（吸気冷却装置）10を備えているエンジン１
の場合において、ＥＧＲガスｇをインタークーラ10上流
の吸気管路５に戻して、吸気空気ａとともにインターク
ーラ10で冷却空気Ａを用いて冷却する方法がある。Then, in order to cool the EGR gas, as shown in FIG.
As shown in FIG. 4, a water-cooled EGR cooler 12 is installed in the EGR pipe line 7 that connects the exhaust manifold 2 and the intake pipe line 5, and the cooling water W is used to cool the EGR gas g. Thus, the engine 1 having the intercooler (intake cooling device) 10 for cooling the intake air a in the intake pipe line 5 connecting the compressor 4b of the supercharger 4 and the intake manifold 3
In this case, there is a method in which the EGR gas g is returned to the intake pipe line 5 upstream of the intercooler 10 and the cooling air A is used in the intercooler 10 together with the intake air a.
【０００５】[0005]
【発明が解決しようとする課題】しかしながら、水冷式
のＥＧＲクーラを用いる場合には、冬季やエンジンスタ
ート直後のように冷却水の温度が低い時に、ＥＧＲガス
が露点以下まで冷却されて、ＥＧＲガス中の水蒸気が結
露し、この結露中にＥＧＲガス中の硫黄酸化物が溶けて
硫酸を生じて、ＥＧＲクーラ、配管及びエンジン内部が
腐食される。そして、この硫酸腐食によってＥＧＲクー
ラの熱交換用パイプに孔が開くと、吸気配管内に冷却水
が漏出して、シリンダ内に入り込み、重大な破損を引き
起こすという問題がある。However, when a water-cooled EGR cooler is used, the EGR gas is cooled to a temperature below the dew point when the temperature of the cooling water is low, such as in winter or immediately after the engine starts. The water vapor therein condenses, and the sulfur oxides in the EGR gas melt during the condensation to generate sulfuric acid, which corrodes the EGR cooler, the pipes, and the inside of the engine. When a hole is opened in the heat exchange pipe of the EGR cooler due to this sulfuric acid corrosion, cooling water leaks into the intake pipe and enters the cylinder, causing serious damage.
【０００６】また、ＥＧＲガスから放熱された熱量をラ
ジエータを通る冷却水へ逃がすために、結果的にラジエ
ータの放熱における負担が大きくなるという問題と、水
冷方式のため装置が複雑化し、また重くなるという問題
がある。一方、インタークーラ内でＥＧＲガスと吸気空
気の混合気を冷却する場合においても、ＥＧＲガスに
は、水蒸気や硫黄酸化物が含まれているため、過冷却に
よって生じる結露に起因する硫酸腐食の問題があり、ま
た、高温のＥＧＲガスが吸気空気に加わり、インターク
ーラに入る混合気は温度が上昇して体積が増加するの
で、インタークーラにおける混合気の通過抵抗が増加す
るという問題もある。Further, since the amount of heat radiated from the EGR gas is released to the cooling water passing through the radiator, the problem that the radiator radiates heat becomes large, and the water cooling system complicates the device and makes it heavy. There is a problem. On the other hand, even when the mixture of EGR gas and intake air is cooled in the intercooler, since the EGR gas contains water vapor and sulfur oxides, there is a problem of sulfuric acid corrosion caused by dew condensation caused by supercooling. In addition, since the high temperature EGR gas is added to the intake air and the temperature of the air-fuel mixture entering the intercooler rises and the volume increases, there is also a problem that the passage resistance of the air-fuel mixture in the intercooler increases.
【０００７】本発明は、上述の問題を解決するためにな
されたもので、その目的とするところは、吸気冷却装置
に入る前に、ＥＧＲガスと吸気空気とで熱交換し、吸気
冷却装置の放熱効果を大きくして、吸気冷却装置下流で
合流するＥＧＲガスと吸気空気との混合気の温度低下量
を大きくすることができるので、ＮＯx を低減するため
にＥＧＲ率を高くしても、空気量を確保してスモークを
少なくでき、更に、ラジエターでの放熱量の増加と結露
による硫酸腐食とを防止できる軽量のディーゼルエンジ
ン用ＥＧＲ装置を提供することである。The present invention has been made in order to solve the above-mentioned problems, and the purpose of the present invention is to exchange heat between EGR gas and intake air before entering the intake cooling device so that the intake cooling device Since it is possible to increase the heat dissipation effect and increase the amount of temperature decrease of the mixture of EGR gas and intake air that merges downstream of the intake air cooling device, even if the EGR rate is increased to reduce NOx, the air It is an object of the present invention to provide a lightweight EGR device for a diesel engine that can secure a sufficient amount to reduce smoke, and further, can prevent an increase in heat radiation in a radiator and sulfuric acid corrosion due to dew condensation.
【０００８】[0008]
【課題を解決するための手段】以上のような目的を達成
するために、過給機付ディーゼルエンジンの該過給機の
コンプレッサから吸気マニホールドに至る吸気管路に吸
気冷却装置を配設し、更に前記吸気冷却装置の上流側に
熱交換器を直列的に配置し、排気マニホールドから前記
吸気冷却装置の下流側の吸気管路に至るＥＧＲ弁を有す
るＥＧＲ管を該熱交換器の高温流体通路に接続し、前記
吸気冷却装置の上流側において吸気空気とＥＧＲガスと
で熱交換するように構成したディーゼルエンジン用ＥＧ
Ｒ装置を提供する。In order to achieve the above object, an intake air cooling device is provided in an intake pipe line of a diesel engine with a supercharger from a compressor of the supercharger to an intake manifold, Further, a heat exchanger is arranged in series on the upstream side of the intake air cooling device, and an EGR pipe having an EGR valve extending from an exhaust manifold to an intake pipe line on the downstream side of the intake air cooling device is connected to a high temperature fluid passage of the heat exchanger. And an EG for a diesel engine configured to exchange heat between intake air and EGR gas on the upstream side of the intake cooling device.
An R device is provided.
【０００９】[0009]
【発明の実施の形態】以下、図面を用いて、本発明の実
施形態を説明する。図１は、本発明の第１の実施の形態
に係わるＥＧＲ装置の構成を示し、エンジン１に過給機
（ターボチャージャ）４が設けられ、従動側のコンプレ
ッサ４ｂから該エンジン１の吸気マニホールド３に至る
吸気管路５に、吸気冷却装置（インタークーラ）10を配
設してある。そして、更に、この吸気冷却装置10の上流
側に熱交換器（ＥＧＲクーラ）９を直列的に配置し、吸
気空気ａは、この熱交換機の低温流体通路９ｂと吸気冷
却装置10を順に経由して該エンジン１の吸気マニホール
ド３に供給される。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a configuration of an EGR device according to a first embodiment of the present invention, in which an engine 1 is provided with a supercharger (turbocharger) 4 and a driven side compressor 4b to an intake manifold 3 of the engine 1. An intake air cooling device (intercooler) 10 is arranged in the intake pipe line 5 leading to. Further, a heat exchanger (EGR cooler) 9 is arranged in series on the upstream side of the intake air cooling device 10, and the intake air a passes through the low temperature fluid passage 9b of the heat exchanger and the intake air cooling device 10 in order. Is supplied to the intake manifold 3 of the engine 1.
【００１０】また、ＥＧＲを行うために、エンジン１の
排気マニホールド２から、吸気冷却装置10の下流側の吸
気管路５に至るＥＧＲ弁６を有するＥＧＲ管７を設けて
あり、このＥＧＲ管７を熱交換器９の高温流体通路９ａ
に接続し、ＥＧＲガスｇは、図示されていないコントロ
ーラによる制御を受けて弁の開閉度を調整するＥＧＲ弁
６によって、ガス流量を調整され、熱交換器９の高温流
体通路９ａを経由して、該エンジン１の吸気マニホール
ド３に供給される。Further, in order to perform EGR, an EGR pipe 7 having an EGR valve 6 extending from the exhaust manifold 2 of the engine 1 to the intake pipe line 5 on the downstream side of the intake cooling device 10 is provided, and the EGR pipe 7 is provided. The high temperature fluid passage 9a of the heat exchanger 9
The EGR gas g is controlled by a controller (not shown) to adjust the opening / closing degree of the valve so that the EGR gas g has its gas flow rate adjusted and passes through the high temperature fluid passage 9a of the heat exchanger 9. , To the intake manifold 3 of the engine 1.
【００１１】そして、吸気冷却装置10の上流側の熱交換
器９において、低温流体通路９ｂを通過する吸気空気ａ
と高温流体通路９ａを通過するＥＧＲガスｇとの間で熱
交換を行い、吸気空気ａを加熱し、ＥＧＲガスｇを冷却
する。以上のような構成により、エンジン１の排気出口
管路14から排出される排気ガスＧが過給機４のタ─ビン
４ａを駆動し、従動側のコンプレサー４ｂにより、吸気
空気ａが吸気入口管路13から吸引されて加圧される。In the heat exchanger 9 on the upstream side of the intake air cooling device 10, the intake air a passing through the low temperature fluid passage 9b.
And the EGR gas g passing through the high temperature fluid passage 9a are exchanged with each other to heat the intake air a and cool the EGR gas g. With the above-described configuration, the exhaust gas G discharged from the exhaust outlet pipe line 14 of the engine 1 drives the turbine 4a of the supercharger 4, and the driven side compressor 4b changes the intake air a into the intake inlet pipe. It is sucked from the passage 13 and pressurized.
【００１２】この保有熱量Ｑａの吸気空気ａは、吸気管
路５に設けられた熱交換器９の低温流体側の通路を通っ
て、ＥＧＲガスｇと熱量Ｑｂを熱交換し温度上昇して熱
保有量が（Ｑａ＋Ｑｂ）になった後、吸気冷却装置10に
入って、冷却空気Ａによって冷却されて、熱保有量が
（Ｑａ＋Ｑｂ−Ｑｃ）になって、吸気マニホールド３に
供給される。The intake air a having the stored heat quantity Qa passes through the passage on the low temperature fluid side of the heat exchanger 9 provided in the intake pipe line 5, exchanges heat between the EGR gas g and the heat quantity Qb to increase the temperature and heat. After the holding amount becomes (Qa + Qb), it enters the intake air cooling device 10 and is cooled by the cooling air A, and the heat holding amount becomes (Qa + Qb−Qc) and is supplied to the intake manifold 3.
【００１３】なお、ここに記載の熱量の変化に関して
は、説明を簡便にするために、各配管や熱交換器やイン
タークーラなどに於ける熱損失を無視している。一方、
ＥＧＲ弁６でガス量を調整された熱保有量ＱｇのＥＧＲ
ガスｇは、排気マニホールド２から、ＥＧＲ管路７の途
中に設けられた熱交換器９の高温流体側の通路を通っ
て、吸気空気ａと熱交換して温度低下して熱保有量が
（Ｑｇ−Ｑｂ）になった後、インタークーラ10の下流の
吸気配管５に供給され、吸気空気ａと混合されて吸気マ
ニホールド３に入る。Regarding the change in the amount of heat described here, the heat loss in each pipe, the heat exchanger, the intercooler, etc. is neglected in order to simplify the explanation. on the other hand,
EGR of heat holding amount Qg whose gas amount is adjusted by the EGR valve 6
The gas g passes through the passage on the high temperature fluid side of the heat exchanger 9 provided in the middle of the EGR pipe 7 from the exhaust manifold 2, exchanges heat with the intake air a to lower the temperature, and the heat retention amount becomes ( After becoming Qg-Qb), it is supplied to the intake pipe 5 downstream of the intercooler 10, mixed with intake air a, and enters the intake manifold 3.
【００１４】このように、吸気冷却装置10に入る吸気空
気ａの温度を上昇させて、吸気空気ａと冷却空気Ａとの
温度差を大きくできるので、この温度差に略比例する熱
交換量（放熱量）Ｑｃも大きくできて、吸気空気ａに対
する冷却効果を向上できる。次に、吸気空気ａとＥＧＲ
ガスｇとの混合気に対する冷却効果を明確にするため
に、吸気マニホールド３に入る混合気の熱量について、
配管や熱交換器などの熱損失を無視して単純化して表現
すると、吸気マニホールド３に入る吸気空気ａの保有熱
量は（Ｑａ＋Ｑｂ−Ｑｃ）で、ＥＧＲガスｇの保有熱量
は（Ｑｇ−Ｑｂ）であるので、吸気マニホールド３に入
る混合気の熱量は（Ｑｇ＋Ｑａ−Ｑｃ）となる。As described above, the temperature difference between the intake air a and the cooling air A can be increased by raising the temperature of the intake air a entering the intake air cooling device 10. Therefore, the amount of heat exchange ( The heat radiation amount) Qc can also be increased, and the cooling effect on the intake air a can be improved. Next, intake air a and EGR
In order to clarify the cooling effect on the air-fuel mixture with the gas g, regarding the heat quantity of the air-fuel mixture entering the intake manifold 3,
If it is simplified and expressed by ignoring the heat loss of the pipes and the heat exchanger, the retained heat amount of the intake air a entering the intake manifold 3 is (Qa + Qb−Qc), and the retained heat amount of the EGR gas g is (Qg−Qb). Therefore, the heat quantity of the air-fuel mixture entering the intake manifold 3 is (Qg + Qa−Qc).
【００１５】つまり、吸気冷却装置10の放熱量Ｑｃを大
きくするほど、吸気マニホールド３に入る混合気の熱量
は小さくなり、混合気の温度も低くなることがわかる。
以上のように、本実施の形態により、過給機付ディーゼ
ルエンジンの吸気冷却装置10の上流において、吸気空気
ａとＥＧＲガスｇとの間で熱交換して吸気空気ａの温度
を上昇させて、吸気冷却装置10の放熱効率を大きくでき
る。従って、吸気マニホールド３に入るＥＧＲガスｇと
吸気空気ａとの混合気の温度を低下させることができ、
ＥＧＲ率を高めてＮＯx を低減しながら、空気量を確保
してスモークを少なくできる。That is, it can be seen that as the heat radiation amount Qc of the intake air cooling device 10 is increased, the heat amount of the air-fuel mixture entering the intake manifold 3 becomes smaller and the temperature of the air-fuel mixture becomes lower.
As described above, according to the present embodiment, heat is exchanged between the intake air a and the EGR gas g to raise the temperature of the intake air a upstream of the intake air cooling device 10 of the diesel engine with a supercharger. The heat radiation efficiency of the intake air cooling device 10 can be increased. Therefore, the temperature of the mixture of EGR gas g and intake air a entering the intake manifold 3 can be lowered,
The amount of air can be secured and smoke can be reduced while increasing the EGR rate and reducing NOx.
【００１６】そして、従来技術の水冷式ＥＧＲクーラに
比べると次の効果が得られる。熱交換器９の冷却側の吸
気空気ａの温度は、冷却水Ｗの温度に比べて高いので、
ＥＧＲガスｇが露点以下まで冷却されることを無くすこ
とができて、ＥＧＲガスｇ中の水蒸気が結露することを
防止でき、硫酸腐食を避けることができる。また、冷却
水Ｗに放熱しないのでラジエターの負担を軽減でき、そ
の上、稼働時の装置重量も水冷式に比較して軽くでき
る。The following effects can be obtained as compared with the conventional water-cooled EGR cooler. Since the temperature of the intake air a on the cooling side of the heat exchanger 9 is higher than the temperature of the cooling water W,
It is possible to prevent the EGR gas g from being cooled to a temperature below the dew point, prevent condensation of water vapor in the EGR gas g, and avoid sulfuric acid corrosion. Further, since the heat is not radiated to the cooling water W, the load on the radiator can be reduced, and the weight of the device during operation can be reduced as compared with the water cooling type.
【００１７】次に、ＥＧＲガスを、吸気空気ａと共にイ
ンタークーラ（吸気冷却装置）10内で冷却する方式に比
べると次の効果が得られる。本実施の形態の吸気冷却装
置９においては、燃焼によって生じた水蒸気分と硫黄酸
化物を含むＥＧＲガスｇが、吸気冷却装置10内に入らな
いので、吸気空気ａが過度に冷却されても結露の発生は
少なく、また、例え結露しても硫黄酸化物が含まれない
ので硫酸腐食は発生しない。Next, the following effects are obtained as compared with the system in which the EGR gas is cooled in the intercooler (intake air cooling device) 10 together with the intake air a. In the intake air cooling device 9 of the present embodiment, the EGR gas g containing water vapor and sulfur oxides generated by combustion does not enter the intake air cooling device 10, so that even if the intake air a is excessively cooled, dew condensation occurs. Sulfuric acid corrosion does not occur because even if dew condensation occurs, sulfur oxides are not included.
【００１８】また、熱交換器９においても、ＥＧＲガス
ｇは、吸気加圧されて温度が上昇した吸気空気ａとの熱
交換することになるので、冷却水Ｗで冷却された場合と
異なり、露点以下まで冷却されることはなく硫酸腐食の
問題も生じない。次に、第２の実施の形態を図２に示
す。この実施の形態では、吸気冷却装置10の入口側ヘッ
ダー11内に熱交換用の高温流体通路９ａを設け、この高
温流体通路９ａにＥＧＲガス管路７を接続し、吸気空気
ａとＥＧＲガスｇとの熱交換をこの入口側ヘッダー11内
で行う。Also in the heat exchanger 9, since the EGR gas g exchanges heat with the intake air a whose intake pressure is increased and its temperature has risen, unlike the case where the EGR gas g is cooled by the cooling water W, It is not cooled below the dew point, and there is no problem of sulfuric acid corrosion. Next, a second embodiment is shown in FIG. In this embodiment, a high temperature fluid passage 9a for heat exchange is provided in the inlet side header 11 of the intake air cooling device 10, the EGR gas pipe 7 is connected to the high temperature fluid passage 9a, and the intake air a and the EGR gas g are connected. Heat is exchanged with the inside of the header 11 on the inlet side.
【００１９】このように構成することで、第１の実施の
形態の効果に加えて、装置全体をコンパクトかつ軽量化
できるので、狭いエンジンスペースでも容易に設置でき
るという効果を奏することができる。With such a configuration, in addition to the effects of the first embodiment, the entire apparatus can be made compact and lightweight, so that it can be easily installed even in a narrow engine space.
【００２０】[0020]
【発明の効果】請求項１の本発明により、吸気冷却装置
に入る前に、ＥＧＲガスと吸気空気とで熱交換し、吸気
冷却装置の放熱効果を大きくして、吸気冷却装置下流で
合流するＥＧＲガスと吸気空気との混合気の温度低下量
を大きくすることができるので、ＮＯx を低減するため
にＥＧＲ率を高くしても、空気量を確保してスモークを
少なくできる。そして、ＥＧＲガスの冷却に吸気空気を
用い、また、吸気冷却装置では、ＥＧＲガスとの熱交換
により温度上昇した吸気空気のみを冷却するので、ラジ
エターでの放熱量の増加と結露による硫酸腐食とを防止
できる軽量のディーゼルエンジン用ＥＧＲ装置を得るこ
とができる。According to the first aspect of the present invention, the heat is exchanged between the EGR gas and the intake air before entering the intake air cooling device, the heat radiation effect of the intake air cooling device is increased, and the heat is merged in the downstream side of the intake air cooling device. Since the temperature decrease amount of the mixture of EGR gas and intake air can be increased, even if the EGR rate is increased to reduce NOx, the air amount can be secured and smoke can be reduced. The intake air is used to cool the EGR gas, and the intake air cooling device cools only the intake air whose temperature has risen due to heat exchange with the EGR gas. Therefore, the amount of heat released by the radiator increases and sulfuric acid corrosion due to dew condensation occurs. It is possible to obtain a lightweight EGR device for a diesel engine that can prevent the above.
【図１】本発明の第１の実施の形態を示すＥＧＲ装置の
構成図である。FIG. 1 is a configuration diagram of an EGR device showing a first embodiment of the present invention.
【図２】本発明の第２の実施の形態を示すＥＧＲ装置の
構成図である。FIG. 2 is a configuration diagram of an EGR device showing a second embodiment of the present invention.
【図３】従来における水冷式ＥＧＲクーラを使用してい
るＥＧＲ装置の構成図である。FIG. 3 is a configuration diagram of an EGR device using a conventional water-cooled EGR cooler.
【図４】従来におけるインタークーラを使用しているＥ
ＧＲ装置の構成図である。FIG. 4 E using a conventional intercooler
It is a block diagram of a GR apparatus.
１ エンジン ２ 排気マニホールド ３ 吸気マニホールド ４ 過給機（ターボチャ
ージャ） ４ａ タービン ４ｂ コンプレッサ ５ 吸気管路 ６ ＥＧＲ弁 ７ ＥＧＲ管路 ９ 熱交換器 ９ａ 高温流体通路 ９ｂ 低温流体通路 10 吸気冷却手段 11 入口側ヘッダー 12 ＥＧＲクーラ 13 吸気入口管路 14 排気出口管路1 Engine 2 Exhaust Manifold 3 Intake Manifold 4 Supercharger (Turbocharger) 4a Turbine 4b Compressor 5 Intake Pipeline 6 EGR Valve 7 EGR Pipeline 9 Heat Exchanger 9a High Temperature Fluid Passage 9b Low Temperature Fluid Passage 10 Inlet Cooling Unit 11 Inlet Side Header 12 EGR cooler 13 Intake inlet line 14 Exhaust outlet line
Claims (1)
（１）の該過給機（４）のコンプレッサ（４ｂ）から吸
気マニホールド（３）に至る吸気管路（５）に吸気冷却
装置（10）を配設し、更に前記吸気冷却装置（10）の上
流側に熱交換器（９）を直列的に配置し、排気マニホー
ルド（２）から前記吸気冷却装置（10）の下流側の吸気
管路（５）に至るＥＧＲ弁（６）を有するＥＧＲ管
（７）を該熱交換器（９）の高温流体通路（９ａ）に接
続し、前記吸気冷却装置（10）の上流側において吸気空
気（ａ）とＥＧＲガス（ｇ）とで熱交換するように構成
したディーゼルエンジン用ＥＧＲ装置。1. An intake air cooling device (10) in an intake pipe (5) extending from a compressor (4b) of the supercharger (4) of a diesel engine (1) with a supercharger (4) to an intake manifold (3). ) Is arranged, and further, a heat exchanger (9) is arranged in series on the upstream side of the intake cooling device (10), and an intake pipe from the exhaust manifold (2) to the downstream side of the intake cooling device (10). An EGR pipe (7) having an EGR valve (6) leading to a passage (5) is connected to a high temperature fluid passage (9a) of the heat exchanger (9), and intake air is provided upstream of the intake cooling device (10). An EGR device for a diesel engine configured to perform heat exchange between (a) and EGR gas (g).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8094079A JPH09280118A (en) | 1996-04-16 | 1996-04-16 | Egr device for diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8094079A JPH09280118A (en) | 1996-04-16 | 1996-04-16 | Egr device for diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09280118A true JPH09280118A (en) | 1997-10-28 |
Family
ID=14100488
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8094079A Pending JPH09280118A (en) | 1996-04-16 | 1996-04-16 | Egr device for diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09280118A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2847004A1 (en) * | 2002-11-12 | 2004-05-14 | Peugeot Citroen Automobiles Sa | Temperature regulation for engine intake air and recirculated exhaust gas, uses single unit housing two heat exchangers to exchange heat between exhaust gas, fluid and intake air, with control of fluid flow |
| EP1586845A1 (en) * | 2004-04-15 | 2005-10-19 | Modine Manufacturing Company | Exhaust gas heat exchanger |
| JP2008540929A (en) * | 2005-05-18 | 2008-11-20 | スカニア シーブイ アクチボラグ（パブル） | Exhaust gas recirculation device for a supercharged internal combustion engine |
| WO2010126402A1 (en) | 2009-04-28 | 2010-11-04 | Volvo Lastvagnar Ab | Cooler arrangement, a cooler and vehicle comprising the cooler arrangement |
| US7921648B2 (en) * | 2005-02-21 | 2011-04-12 | Behr Gmbh & Co. Kg | Exhaust gas turbocharger internal combustion engine |
| KR101490963B1 (en) * | 2013-12-11 | 2015-02-06 | 현대자동차 주식회사 | Engine system having turbo charger |
| KR101534725B1 (en) * | 2013-12-06 | 2015-07-07 | 현대자동차 주식회사 | Engine system having turbo charger |
| CN109695494A (en) * | 2017-10-24 | 2019-04-30 | 翰昂汽车零部件有限公司 | Gas recovery system |
| KR102139573B1 (en) * | 2019-02-21 | 2020-07-30 | 동명대학교산학협력단 | Condensate water discharge device of low pressure EGR system |
| CN114810330A (en) * | 2021-06-01 | 2022-07-29 | 长城汽车股份有限公司 | Intercooling control method and device for diesel vehicle and vehicle |
| CN114901932A (en) * | 2020-01-23 | 2022-08-12 | 日产自动车株式会社 | Cooling device for vehicle |
-
1996
- 1996-04-16 JP JP8094079A patent/JPH09280118A/en active Pending
Cited By (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2847004A1 (en) * | 2002-11-12 | 2004-05-14 | Peugeot Citroen Automobiles Sa | Temperature regulation for engine intake air and recirculated exhaust gas, uses single unit housing two heat exchangers to exchange heat between exhaust gas, fluid and intake air, with control of fluid flow |
| WO2004044402A1 (en) * | 2002-11-12 | 2004-05-27 | Peugeot Citroen Automobiles S.A. | Device for the thermal regulation of the intake air for an engine and the recirculated exhaust gas emitted by said engine. |
| EP1586845A1 (en) * | 2004-04-15 | 2005-10-19 | Modine Manufacturing Company | Exhaust gas heat exchanger |
| US7703506B2 (en) | 2004-04-15 | 2010-04-27 | Modine Manufacturing Company | Exhaust heat exchanger |
| US7921648B2 (en) * | 2005-02-21 | 2011-04-12 | Behr Gmbh & Co. Kg | Exhaust gas turbocharger internal combustion engine |
| JP2008540929A (en) * | 2005-05-18 | 2008-11-20 | スカニア シーブイ アクチボラグ（パブル） | Exhaust gas recirculation device for a supercharged internal combustion engine |
| WO2010126402A1 (en) | 2009-04-28 | 2010-11-04 | Volvo Lastvagnar Ab | Cooler arrangement, a cooler and vehicle comprising the cooler arrangement |
| EP2425112A4 (en) * | 2009-04-28 | 2015-12-16 | Volvo Lastvagnar Ab | Cooler arrangement, a cooler and vehicle comprising the cooler arrangement |
| KR101534725B1 (en) * | 2013-12-06 | 2015-07-07 | 현대자동차 주식회사 | Engine system having turbo charger |
| US9435296B2 (en) | 2013-12-06 | 2016-09-06 | Hyundai Motor Company | Engine system having turbocharger |
| KR101490963B1 (en) * | 2013-12-11 | 2015-02-06 | 현대자동차 주식회사 | Engine system having turbo charger |
| CN109695494A (en) * | 2017-10-24 | 2019-04-30 | 翰昂汽车零部件有限公司 | Gas recovery system |
| KR20190045853A (en) * | 2017-10-24 | 2019-05-03 | 한온시스템 주식회사 | Exhaust gas recirculation system |
| US11060488B2 (en) | 2017-10-24 | 2021-07-13 | Hanon Systems | Exhaust gas recirculation system |
| CN109695494B (en) * | 2017-10-24 | 2022-09-20 | 翰昂汽车零部件有限公司 | Waste gas recovery system |
| KR102139573B1 (en) * | 2019-02-21 | 2020-07-30 | 동명대학교산학협력단 | Condensate water discharge device of low pressure EGR system |
| CN114901932A (en) * | 2020-01-23 | 2022-08-12 | 日产自动车株式会社 | Cooling device for vehicle |
| CN114901932B (en) * | 2020-01-23 | 2023-07-28 | 日产自动车株式会社 | Cooling device for vehicle |
| CN114810330A (en) * | 2021-06-01 | 2022-07-29 | 长城汽车股份有限公司 | Intercooling control method and device for diesel vehicle and vehicle |
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