JPS5930905B2 - EGR control method for supercharged diesel engine - Google Patents
EGR control method for supercharged diesel engineInfo
- Publication number
- JPS5930905B2 JPS5930905B2 JP53056342A JP5634278A JPS5930905B2 JP S5930905 B2 JPS5930905 B2 JP S5930905B2 JP 53056342 A JP53056342 A JP 53056342A JP 5634278 A JP5634278 A JP 5634278A JP S5930905 B2 JPS5930905 B2 JP S5930905B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- exhaust
- egr
- compressor
- diesel engine
- 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.)
- Expired
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
- 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
- F02M26/07—Mixed pressure loops, i.e. wherein recirculated exhaust gas is either taken out upstream of the turbine and reintroduced upstream of the compressor, or is taken out downstream of the turbine and reintroduced 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
- F02M26/02—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
- F02M26/38—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with two or more EGR valves disposed in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/04—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning exhaust conduits
-
- 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
- F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
- F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Description
【発明の詳細な説明】
本発明は過給式ディーゼルエンジンにおいて、ＥＧＲを
効果的に行う制御方法に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a control method for effectively performing EGR in a supercharged diesel engine.
過給式ディーゼルエンジンでＥＧＲを行う場合、ＥＧＲ
率のコントロールが困難である。When performing EGR on a supercharged diesel engine, EGR
It is difficult to control the rate.
さらに、ＥＧＲガスはコンプレッサに入る前の吸気系に
導入させる方が制御および構造が簡単となるが、その反
面、ＥＧＲガスがコンプレッサを通過する際、コンプレ
ッサを汚染させ、耐久性を低下させる。Furthermore, although it is easier to control and structure the EGR gas by introducing it into the intake system before entering the compressor, on the other hand, when the EGR gas passes through the compressor, it contaminates the compressor and reduces its durability.
他方、ＥＧＲガスをコンプレッサを出た後の吸気系に導
入させると、該コンプレッサを汚染しないが、その反面
では過給圧が排気圧より大きいときにＥＧＲを行い得な
い欠点が生ずる。On the other hand, if EGR gas is introduced into the intake system after exiting the compressor, the compressor will not be contaminated, but on the other hand, there is a drawback that EGR cannot be performed when the boost pressure is greater than the exhaust pressure.
さらにまたＥＧＲ率は吸気に対するＥＧＲガスの割合で
あるが、吸気の流量はエンジン回転数により異なるので
ＥＧＲ率を所定値に維持させるには非常な困難を伴うも
のとなる。Furthermore, the EGR rate is the ratio of EGR gas to the intake air, but since the flow rate of the intake air varies depending on the engine speed, it is extremely difficult to maintain the EGR rate at a predetermined value.
本発明の目的は、コンプレッサの耐久性を向上させ、か
つＥＧＲ率の制御を効果的に行いうる如くしたＥＧＲ制
御方法を提供するにある。An object of the present invention is to provide an EGR control method that can improve the durability of a compressor and effectively control the EGR rate.
第１図を参照して、ディーゼルエンジン１はタービン２
に連動して駆動されるコンプレッサ３を有しており、こ
れによつて過給されている。Referring to FIG. 1, a diesel engine 1 has a turbine 2
It has a compressor 3 that is driven in conjunction with the engine, and is supercharged by this.
吸気は、コンプレッサ３に導入される前の１次吸気系４
とコンプレッサ３を出した後の２次吸気系５とを介して
ディーゼルエンジン１へ吸入される。また、排気は、タ
ービン２に導入される前の１次排気系６とタービン２を
出た後の２次排気系１を介して排出される。以上は、通
常の過給式ディーゼルエンジンであるが本発明では次の
如くＥＧＲがなされる。The intake air is passed through the primary intake system 4 before being introduced into the compressor 3.
The air is sucked into the diesel engine 1 via the secondary intake system 5 after the compressor 3 is discharged. Further, the exhaust gas is exhausted through the primary exhaust system 6 before being introduced into the turbine 2 and the secondary exhaust system 1 after leaving the turbine 2. The above is a normal supercharged diesel engine, but in the present invention, EGR is performed as follows.
１次排気系６と１次吸気系４とを連絡する低圧ＥＧＲ通
路８が設けられ、該低圧ＥＧＲ通路８には弁９が設けら
れる。A low pressure EGR passage 8 is provided that communicates the primary exhaust system 6 and the primary intake system 4, and a valve 9 is provided in the low pressure EGR passage 8.
また、１次排気系６と２次吸気系５を連絡する高圧ＥＧ
Ｒ通路１０が設けられ、該高圧ＥＧＲ通路１０には弁１
１が設けられる。さらに、コントローラ１２は、２次吸
気系５の過給圧と１次排気系６の排気圧との差圧および
エンジン回転数を検出し、弁９あるいは弁１１へ開閉信
号を発するものである。In addition, a high-pressure EG connecting the primary exhaust system 6 and the secondary intake system 5
An R passage 10 is provided, and a valve 1 is provided in the high pressure EGR passage 10.
1 is provided. Furthermore, the controller 12 detects the differential pressure between the supercharging pressure of the secondary intake system 5 and the exhaust pressure of the primary exhaust system 6 and the engine rotational speed, and issues an opening/closing signal to the valve 9 or the valve 11.
上記の如く構成された本発明の作用を説明する。The operation of the present invention configured as described above will be explained.
今、２次吸気系５の過給圧Ｐ４が１次排気系６の排気圧
Ｐ２よりも小さいとするとコントローラ１２は弁９を閉
鎖させ、弁１１を開かせる。弁１１の開度は過給圧Ｐ、
と排気圧Ｐ２との圧差（Ｐ４−Ｐ２）、およびエンジン
回転数（Ｎ）によつて定められ、この弁開度によりＥＧ
Ｒ率を制御する。次に過給圧Ｐ，と排気圧Ｐ２との差圧
が（Ｐ，≧Ｐ２）となつたときには弁１１が閉じ、弁９
が開く。Now, assuming that the supercharging pressure P4 of the secondary intake system 5 is lower than the exhaust pressure P2 of the primary exhaust system 6, the controller 12 closes the valve 9 and opens the valve 11. The opening degree of the valve 11 is the supercharging pressure P,
It is determined by the pressure difference (P4-P2) between the
Control the R rate. Next, when the differential pressure between the boost pressure P and the exhaust pressure P2 becomes (P, ≧P2), the valve 11 closes and the valve 9
opens.
弁９の開度は差圧（Ｐ１−ーーＰ２）により定められ、
この弁開度によりＥＧＲ率を制御する。以上の如く構成
された本発明の一実施例によると次のような効果を奏す
る。The opening degree of the valve 9 is determined by the differential pressure (P1--P2),
The EGR rate is controlled by this valve opening degree. According to one embodiment of the present invention configured as described above, the following effects are achieved.
コンプレッサを通過するＥＧＲガス量を低減しうるので
、コンプレッサの汚染が低減され、耐久性が向上する。Since the amount of EGR gas passing through the compressor can be reduced, contamination of the compressor is reduced and durability is improved.
エンジン回転数（Ｎ）および吸、排気の差圧によりＥＧ
Ｒガス量を決めるのでＥＧＲ率の制御が正確である。EG due to engine speed (N) and differential pressure between intake and exhaust.
Since the amount of R gas is determined, the EGR rate can be controlled accurately.
なお、上記実施例において、２次排気系７に設けられた
弁１３は、該弁１３を絞ることによりＥＧＲガス量を増
加させるものであり、大量のＥＧＲガスを必要とする場
合に有効な手段である。In the above embodiment, the valve 13 provided in the secondary exhaust system 7 increases the amount of EGR gas by throttling the valve 13, and is an effective means when a large amount of EGR gas is required. It is.
以上は本発明の一実施例であり、本発明は次のようにす
ることもある。過給式ディーゼルエンジンでは、過給圧
（Ｐ１）と排気圧（Ｐ２）との差圧（Ｐ１−Ｐ２）の値
は、エンジンの負荷によつて異なる。The above is one embodiment of the present invention, and the present invention may also be implemented as follows. In a supercharged diesel engine, the value of the differential pressure (P1-P2) between supercharging pressure (P1) and exhaust pressure (P2) varies depending on the engine load.
第２図はエンジン回転数（Ｎ）と負荷（Ｌ）の特性を示
す線図であり、図からもわかるとおり、負荷（Ｌ）が大
きい程差圧（Ｐ１−Ｐ２）が大きくなるがエンジン回転
数（Ｎ）によつては、大きくは変化しない。Figure 2 is a diagram showing the characteristics of engine speed (N) and load (L).As can be seen from the figure, the larger the load (L), the larger the differential pressure (P1-P2), but the engine speed It does not change much depending on the number (N).
また、ＥＧＲガスは高負荷時にカットして出力向上をは
かることが望ましい。Further, it is desirable to cut EGR gas at high loads to improve output.
今、ＥＧＲガスをカットする負荷を例へば７／８Ｌとす
ると、第２図のＣの域がＥＧＲカット域となりこのＥＧ
Ｒカット域は差圧（Ｐ１−Ｐ２）とエンジン回転数によ
り略々決定されるものとなる。For example, if the load to cut EGR gas is 7/8L, area C in Figure 2 is the EGR cut area.
The R cut range is approximately determined by the differential pressure (P1-P2) and the engine speed.
そこで、コントロー引２により、差圧【Ｐ１−Ｐ２）お
よび回転数（Ｎ）を検出し、前記Ｃの領域となつた場合
に弁９および弁１１の両者を閉鎖させるように制御する
。Therefore, the differential pressure [P1-P2) and the rotation speed (N) are detected by the controller pull 2, and when the pressure falls within the range C, both the valve 9 and the valve 11 are controlled to be closed.
上記の制御方式によると、高負荷域でのＥＧＲガスのカ
ットが正確に行われる。According to the above control method, EGR gas is accurately cut in a high load range.
このため高出力が必要な場合にＥＧＲによる出力低下が
なく、出力性能を損うことがない。Therefore, when high output is required, there is no output reduction due to EGR, and output performance is not impaired.
第１図は本発明の一実施例を示す系統図である。
第２図はエンジン回転数一負荷特性曲線図である。１・
・・・・・エンジン、２・・・・・・タービン、３・・
・・・・コンプレッサ、４・・・・・・１次吸気系、５
・・・・・・２次吸気系、６・・・・・・１次排気系、
８・・・・・・低圧ＥＧＲ通路、９・・・・・・弁、１
０・・・・・・高圧ＥＧＲ通路、１１・・・・・・弁、
１２・・・・・・コントローラ。FIG. 1 is a system diagram showing one embodiment of the present invention. FIG. 2 is an engine speed-load characteristic curve diagram. 1・
...Engine, 2...Turbine, 3...
...Compressor, 4...Primary intake system, 5
...Secondary intake system, 6...Primary exhaust system,
8...Low pressure EGR passage, 9...Valve, 1
0... High pressure EGR passage, 11... Valve,
12... Controller.
Claims (1)
り駆動されるコンプレッサと、該コンプレッサに導入さ
れる前の１次吸気系と、コンプレッサを出た後の２次吸
気系と、タービンに導入される前の１次排気系と、ター
ビンを出た後の２次排気系とからなる過給式ディーゼル
エンジンにおいて、排気圧と過給圧との差圧およびエン
ジン回転数を検出し、排気圧が高いときには１次排気系
と２次吸気系を連絡し、排気圧が低いときには１次排気
系を１次吸気系とを連絡するようにした夫々の連絡通路
に設けられた弁の開度を差圧およびエンジン回転数（Ｎ
）により設定した過給式ディーゼルエンジンのＥＧＲ制
御方法。1 A turbine driven by exhaust gas, a compressor driven by the turbine, a primary intake system before being introduced into the compressor, a secondary intake system after leaving the compressor, and before being introduced into the turbine. In a supercharged diesel engine, which consists of a primary exhaust system and a secondary exhaust system after exiting the turbine, the differential pressure between exhaust pressure and boost pressure and engine speed are detected, and when the exhaust pressure is high, The opening degree of the valve provided in each communication passage is connected to the primary exhaust system and the secondary intake system, and when the exhaust pressure is low, the primary exhaust system is connected to the primary intake system. Engine speed (N
) EGR control method for a supercharged diesel engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP53056342A JPS5930905B2 (en) | 1978-05-12 | 1978-05-12 | EGR control method for supercharged diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP53056342A JPS5930905B2 (en) | 1978-05-12 | 1978-05-12 | EGR control method for supercharged diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS54148927A JPS54148927A (en) | 1979-11-21 |
| JPS5930905B2 true JPS5930905B2 (en) | 1984-07-30 |
Family
ID=13024544
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP53056342A Expired JPS5930905B2 (en) | 1978-05-12 | 1978-05-12 | EGR control method for supercharged diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5930905B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62137386U (en) * | 1986-02-24 | 1987-08-29 | ||
| JPS62279279A (en) * | 1986-05-28 | 1987-12-04 | Toyooki Kogyo Co Ltd | Hydraulic pump device |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55116863U (en) * | 1979-02-09 | 1980-08-18 | ||
| JPH02123272A (en) * | 1988-10-31 | 1990-05-10 | Suzuki Motor Co Ltd | Exhaust gas recirculation device for engine |
| DE4416572C1 (en) * | 1994-05-11 | 1995-04-27 | Daimler Benz Ag | Turbocharged internal combustion engine |
| SE519433C2 (en) * | 1997-07-07 | 2003-02-25 | Scania Cv Ab | Housing for turbocharger for internal combustion engine and turbocharger |
| US6321536B1 (en) | 2000-12-07 | 2001-11-27 | Cummins Engine Company, Inc. | Pneumatically controlled exhaust throttle for delivering EGR on turbocharged engines |
| US6526752B2 (en) | 2001-01-31 | 2003-03-04 | Cummins, Inc. | Passive engine exhaust flow restriction arrangement |
| US7152393B2 (en) | 2002-07-18 | 2006-12-26 | Daimlerchrysler Ag. | Arrangement for utilizing the throttle energy of an internal combustion engine |
| DE10232516A1 (en) * | 2002-07-18 | 2004-01-29 | Daimlerchrysler Ag | Device for improving the exhaust emission |
| JP4692202B2 (en) * | 2005-10-06 | 2011-06-01 | いすゞ自動車株式会社 | EGR system for two-stage supercharged engine |
| US8206133B2 (en) | 2008-08-12 | 2012-06-26 | GM Global Technology Operations LLC | Turbocharger housing with integral inlet and outlet openings |
| JP6309190B2 (en) * | 2012-12-28 | 2018-04-11 | 三菱重工業株式会社 | Internal combustion engine, ship and method of operating internal combustion engine |
-
1978
- 1978-05-12 JP JP53056342A patent/JPS5930905B2/en not_active Expired
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62137386U (en) * | 1986-02-24 | 1987-08-29 | ||
| JPS62279279A (en) * | 1986-05-28 | 1987-12-04 | Toyooki Kogyo Co Ltd | Hydraulic pump device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS54148927A (en) | 1979-11-21 |
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