JPH0647932B2 - Exhaust gas treatment device for internal combustion engine with turbocharger - Google Patents
Exhaust gas treatment device for internal combustion engine with turbochargerInfo
- Publication number
- JPH0647932B2 JPH0647932B2 JP62145673A JP14567387A JPH0647932B2 JP H0647932 B2 JPH0647932 B2 JP H0647932B2 JP 62145673 A JP62145673 A JP 62145673A JP 14567387 A JP14567387 A JP 14567387A JP H0647932 B2 JPH0647932 B2 JP H0647932B2
- Authority
- JP
- Japan
- Prior art keywords
- exhaust
- exhaust gas
- turbine
- turbocharger
- internal combustion
- 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 - Lifetime
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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features
- F01N13/08—Other arrangements or adaptations of exhaust conduits
- F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
- F01N13/107—More than one exhaust manifold or exhaust collector
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
- F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
- F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
- F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion
- F01N3/2006—Periodically heating or cooling catalytic reactors, e.g. at cold starting or overheating
- F01N3/2033—Periodically heating or cooling catalytic reactors, e.g. at cold starting or overheating using a fuel burner or introducing fuel into exhaust duct
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
- F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
- F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
- F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion
- F01N3/2053—By-passing catalytic reactors, e.g. to prevent overheating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
- F01N2340/00—Dimensional characteristics of the exhaust system, e.g. length, diameter or volume of the exhaust apparatus; Spatial arrangements of exhaust apparatuses
- F01N2340/04—Arrangement of the exhaust system relative to a vehicle or parts thereof
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Health & Medical Sciences (AREA)
- Toxicology (AREA)
- Supercharger (AREA)
- Exhaust Gas After Treatment (AREA)
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明は、２この高圧段排気ターボ化過給機と１個の低
圧段排気ターボ過給機とを有する排気ターボ過給機付内
燃機関の排気ガス処理装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to an internal combustion engine with an exhaust turbocharger having two high pressure exhaust turbochargers and one low pressure exhaust turbocharger. Of the exhaust gas treatment device.
（従来技術及びその問題点） 従来から、多気筒内燃機関に２個の高圧段排気ターボ過
給機と、１個の低圧段排気ターボ過給機とを設けた２段
過給機付内燃機関が知られているが、排気ガス量が少な
い低速時には２個の高圧段タービンを十分に駆動し得る
だけの排気ガス量がなく、タービン効率が低く、過給圧
が不十分である。(Prior Art and its Problems) Conventionally, a two-stage supercharged internal combustion engine in which a multi-cylinder internal combustion engine is provided with two high-pressure exhaust turbochargers and one low-pressure exhaust turbocharger However, there is not enough exhaust gas to drive the two high-pressure stage turbines at a low speed with a small amount of exhaust gas, turbine efficiency is low, and supercharging pressure is insufficient.
また、低速時には燃焼状態が悪く、排気煙や排気臭を除
去することが要望されている。Further, the combustion state is poor at low speed, and it is desired to remove exhaust smoke and exhaust odor.
（発明の目的） 本発明は、低速時の排気浄化と機関性能の向上を両立で
きる排気ターボ過給機付内燃機関の排気ガス処理装置を
提供することを目的としている。(Object of the Invention) An object of the present invention is to provide an exhaust gas treatment device for an internal combustion engine with an exhaust turbocharger, which can achieve both exhaust purification at low speed and improvement of engine performance.
（発明の構成） （１）技術的手段 本発明は、多気筒内燃機関に２個の高圧段排気ターボ過
給機と、１個の低圧段排気ターボ過給機とを設けた２段
過給機付内燃機関において、一方の高圧段排気ターボ過
給機のタービンは、内燃機関の一部の気筒用の排気マニ
ホールドに、一方の排気通路を介して接続し、他方の高
圧段排気ターボ過給機のタービンは、残りの気筒用の排
気マニホールドに他方の排気通路を介して接続し、両排
気通路間にはこれらを接続する接続配管を設け、一方の
排気通路と接続配管との間に切替自在な３方弁を介装
し、他方の排気通路又は該排気通路に他方のタービンを
介して接続する管路の途中に、排気ガスに熱量を追加す
るアフターバーナー装置および排気ガス浄化用の触媒を
設け、排気ガス量の少ない時に前記３方弁で排気ガスを
他方の排気通路に繁がる高圧段排気ターボ過給機だけに
供給するようにした内燃機関の排気ガス処理装置であ
る。(Structure of the Invention) (1) Technical Means The present invention relates to a two-stage supercharge in which a multi-cylinder internal combustion engine is provided with two high pressure exhaust turbochargers and one low pressure exhaust turbocharger. In an engine-equipped internal combustion engine, the turbine of one high-pressure stage exhaust turbocharger is connected to the exhaust manifold for some cylinders of the internal combustion engine via one exhaust passage, and the other high-pressure stage exhaust turbocharger turbocharger. The turbine of the machine is connected to the exhaust manifold for the remaining cylinders via the other exhaust passage, and connecting pipes are provided between both exhaust passages to switch between one exhaust passage and the connecting pipe. An afterburner device for adding heat to the exhaust gas and a catalyst for purifying the exhaust gas are provided in the middle of the other exhaust passage or the conduit connecting to the other exhaust passage via the other turbine via a free three-way valve. Provided, the above 3 directions when the amount of exhaust gas is small In an exhaust gas treatment apparatus of the internal combustion engine so as to supply the exhaust gas only want Shigeru the other exhaust passage pressure stage exhaust turbocharger.
（２）作用 低速時には１個の高圧段排気ターボ過給機だけに排気を
供給して、少ないガス量でタービン効率を上げる。(2) Action At low speed, the exhaust gas is supplied to only one high pressure exhaust turbocharger to increase turbine efficiency with a small amount of gas.
（実施例） （１）第１実施例 本発明を採用した第１実施例のディーゼルエンジンを示
す第１図で、１０は例えば６気筒のディーゼルエンジン
である。ディーゼルエンジン１０は３気筒分づつに吸気
マニホールド１２ａ、１２ｂと排気マニホールド１４
ａ、１４ｂを有している。(Embodiment) (1) First Embodiment In FIG. 1 showing a diesel engine of a first embodiment adopting the present invention, 10 is, for example, a 6-cylinder diesel engine. The diesel engine 10 has intake manifolds 12a and 12b and an exhaust manifold 14 for every three cylinders.
a and 14b.
このデイーゼルエンジン１０には２個の高圧段排気ター
ボ過給機１６ａ、１６ｂと１個に低圧段排気ターボ過給
機２０が設けられている。高圧段過給機１６ａ、１６ｂ
はタービン１８ａ、１８ｂ及びブロワ１９ａ、１９ｂを
備えている。低圧段排気ターボ過給機２０はタービン２
１、ブロワ２２を備えている。排気マニホールド１４ａ
とタービン１８ａは配管２４で接続され、配管２４には
３方弁２６、アフターバーナー装置２８、触媒３０が介
装されている。３方弁２６にはバイパス配管３２が分岐
接続し、バイパス配管３２はアフターバーナー装置２
８、触媒３０をバイパスして触媒３０より下流の配管２
４に分岐接続している。一方、排気マニホールド１４ｂ
とタービン１８ａは配管３４で接続され、配管３４には
３方弁３６が介装されている。３方弁３６には配管２４
と配管３４を繁ぐ接続配管３８が分岐接続している。The diesel engine 10 is provided with two high pressure exhaust turbochargers 16a, 16b and one low pressure exhaust turbocharger 20. High pressure supercharger 16a, 16b
Includes turbines 18a, 18b and blowers 19a, 19b. The low pressure exhaust turbocharger 20 is the turbine 2
1, equipped with a blower 22. Exhaust manifold 14a
The turbine 18a and the turbine 18a are connected by a pipe 24, and the pipe 24 is provided with a three-way valve 26, an afterburner device 28, and a catalyst 30. A bypass pipe 32 is branched and connected to the three-way valve 26, and the bypass pipe 32 is connected to the afterburner device 2
8. Pipe 2 that bypasses the catalyst 30 and is downstream of the catalyst 30
It is branched and connected to 4. On the other hand, the exhaust manifold 14b
And the turbine 18a are connected by a pipe 34, and a three-way valve 36 is interposed in the pipe 34. There is piping 24 for the 3-way valve 36.
And a connection pipe 38 that extends through the pipe 34 is branched and connected.
タービン１８ａ、１８ｂには配管４０が接続し、配管４
０は前記低圧段排気ターボ過給機２０のタービン２１に
繁がっている。タービン２１から排気Ｅが排出されるよ
うになっている。また、ブロワ２２には吸気Ａが吸入さ
れている。A pipe 40 is connected to the turbines 18a and 18b, and a pipe 4
Zero is prominent in the turbine 21 of the low pressure exhaust turbocharger 20. Exhaust gas E is discharged from the turbine 21. Further, the intake air A is drawn into the blower 22.
ブロワ２２には配管４２が接続しており、配管４２はイ
ンタークーラ４４を介して３方弁４６に繁がっている。
３方弁４６には配管４８、５０が接続し、配管４８は前
記高圧段過給機１６ａのブロワ１９ａに繁がり、配管５
０は過給機１６ｂのブロワ１９ｂに繁がっている。A pipe 42 is connected to the blower 22, and the pipe 42 is connected to a three-way valve 46 via an intercooler 44.
Pipes 48 and 50 are connected to the three-way valve 46, and the pipe 48 extends to the blower 19a of the high pressure supercharger 16a, and the pipe 5
0 is proliferating on the blower 19b of the supercharger 16b.
ブロワ１９ａ、１９ｂにはそれぞれ配管５２、５４が接
続し、配管５２、５４はインタークーラ５６を介して吸
気マニホールド１２ａ、１２ｂに過給吸気を供給するよ
うになっている。Pipes 52 and 54 are connected to the blowers 19a and 19b, respectively, and the pipes 52 and 54 supply supercharged intake air to the intake manifolds 12a and 12b via an intercooler 56.
次に作用を説明する。第１図に示す例えばアイドル時等
の低速低負荷時には、ディーゼルエンジン１０から排出
される排気Ｅのガス量が少ないので、２個の高圧段過給
機１６ａ、１６ｂを駆動すると、タービン効率が低下
し、過給圧も低くなる。Next, the operation will be described. At low speed and low load such as at the time of idling shown in FIG. 1, since the gas amount of the exhaust gas E discharged from the diesel engine 10 is small, driving the two high pressure superchargers 16a and 16b lowers the turbine efficiency. However, the boost pressure also becomes low.
そこで、３方弁３６を切換えて排気マニホールド１４
ａ、１４ｂの排気Ｅを接続配管３８から配管２４に集中
し、タービン１８ｂには排気Ｅを供給せず、過給機１６
ｂを停止して高圧団過給機１６ａのタービン１８ａだけ
に排気Ｅを供給する。したがって、タービン１８ａに供
給される排気Ｅのガス量が増えてタービン１８ａのター
ビン効率がよくなる。Therefore, the exhaust manifold 14 is switched by switching the three-way valve 36.
Exhaust gas E of a and 14b is concentrated from the connection pipe 38 to the pipe 24, the exhaust gas E is not supplied to the turbine 18b, and the supercharger 16
Exhaust E is supplied only to the turbine 18a of the high pressure supercharger 16a by stopping b. Therefore, the gas amount of the exhaust gas E supplied to the turbine 18a increases, and the turbine efficiency of the turbine 18a improves.
また、低速低負荷にはディーゼルエンジン１０の燃焼状
態が悪く、排気Ｅの排気煙や排気臭が多いので、３方弁
２６を切換えてアフターバーナー装置２８で排気２８で
排気Ｅに熱量を追加し、触媒３０による排気ガス処理を
促進する。Further, since the combustion state of the diesel engine 10 is poor at low speed and low load, and exhaust smoke and exhaust odor of the exhaust E are large, the heat quantity is added to the exhaust E by the afterburner device 28 by switching the three-way valve 26, The exhaust gas treatment by the catalyst 30 is promoted.
タービン１８ａを駆動した後の排気Ｅはタービン２１を
駆動し、タービン２１はブロワ２２を駆動し、吸気Ａを
圧縮して配管４２、４８からブロワ１９ａで更に圧縮
し、配管５２から吸気マニホールド１２ａ、１２ｂへ過
給吸気を供給する。なお、図中で太線は排気Ｅ又は吸気
Ａが流れている配管を示している。The exhaust gas E after driving the turbine 18a drives the turbine 21, the turbine 21 drives the blower 22, and the intake air A is compressed and further compressed by the blower 19a from the pipes 42 and 48, and the intake manifold 12a from the pipe 52. Supply supercharged intake air to 12b. The thick line in the figure indicates the pipe through which the exhaust gas E or the intake air A flows.
第２図は低高速負荷時には、アフターバーナー装置２８
を作動させつつ排気Ｅのガス量が増えるので、触媒３０
による排気Ｅの流通抵抗が増加し、ディーゼルエンジン
１０の燃費等の性能に悪影響がある。そこで、３方弁２
６を切換えて、排気Ｅを配管２、バイパス配管３２の両
者に流し、バイパス配管３２を通る排気Ｅの分だけター
ビン１８ａの過給能力を上げる。Fig. 2 shows the afterburner device 28 when the load is low and high speed.
Since the gas amount of the exhaust gas E increases while operating the
Due to this, the flow resistance of the exhaust gas E is increased, and the performance of the diesel engine 10 such as fuel consumption is adversely affected. Therefore, 3-way valve 2
6 is switched to flow the exhaust gas E into both the pipe 2 and the bypass pipe 32, and the supercharging capacity of the turbine 18a is increased by the amount of the exhaust gas E passing through the bypass pipe 32.
第３図の高速低負荷時には、排気ガス量が増しディーゼ
ルエンジン１０の燃焼状態が良好になり、アフターバー
ナー装置２８、触媒３０を作動させる必要がなくなるの
で、３方弁２６を切換えてバイパス配管３２だけに排気
Ｅを流し、タービン１８ａに排気Ｅを送る。At the time of high speed and low load in FIG. 3, the exhaust gas amount increases and the combustion state of the diesel engine 10 becomes good, and it is not necessary to operate the afterburner device 28 and the catalyst 30, so the three-way valve 26 is switched and only the bypass pipe 32 is switched. The exhaust gas E is sent to the turbine 18a and is sent to the turbine 18a.
更に第４図の中速高付荷、高速高付荷時には、３方弁３
６を切換えて、配管２４、３４の両者からタービン１８
ａ、１８ｂに排気Ｅを流し、両高圧段過給機１６ａ、１
６ｂを駆動する。この状態では、排気Ｅのガス量が多い
ので、タービン１８ａ、１８ｂのタービン効率が高く、
過給圧も十分に上がる。Furthermore, at the time of medium speed high load and high speed high load in Fig. 4, the 3-way valve 3
6 to switch the turbine 18 from both the pipes 24 and 34.
Exhaust gas E is supplied to a and 18b, and both high pressure superchargers 16a and 1b
Drive 6b. In this state, since the amount of the exhaust gas E is large, the turbine efficiency of the turbines 18a and 18b is high,
Supercharging pressure also rises sufficiently.
（２）第２実施例 第５図に示す第２実施例では、３方弁２６、アフターバ
ーナー装置２８、触媒３０を、タービン１８ａとのター
ビン２１を繁ぐ配管４０ａの途中に介装してある。ター
ビン１８ｂとタービン２１は配管４０ｂで接続してい
る。なお、第５図において、第１図と同一の符号で示し
た部分は同一または相当部分を示す。(2) Second Embodiment In a second embodiment shown in FIG. 5, a three-way valve 26, an afterburner device 28, and a catalyst 30 are provided in the middle of a pipe 40a that is adjacent to the turbine 18a and the turbine 21. . The turbine 18b and the turbine 21 are connected by a pipe 40b. In addition, in FIG. 5, the portions denoted by the same reference numerals as those in FIG. 1 indicate the same or corresponding portions.
この場合では、タービン１８ａに排気マニホールド１４
ａ、１４ｂからの排気Ｅが直接に流れるので、タービン
１８ａの動圧過給効果を損なうことなく流入することに
なり、高圧段過給機１６ａの過給性能が高い。In this case, the exhaust manifold 14 is attached to the turbine 18a.
Since the exhaust gas E from a and 14b directly flows, the exhaust gas E flows in without impairing the dynamic pressure supercharging effect of the turbine 18a, and the supercharging performance of the high pressure supercharger 16a is high.
この第２実施例でも同様に、低速、低負荷時には第５図
のように３方弁２６、３６を切換え、高圧段過給機１６
ａだけを作動して過給機１６ｂを停止する。In the second embodiment as well, at low speed and low load, the three-way valves 26 and 36 are switched as shown in FIG.
Only a is operated and the supercharger 16b is stopped.
また、同様に低速高負荷時には第６図のように３方弁２
６を切換え、高速低負荷時には第７図のように３方弁２
６、３６を切換え、最後に高速高負荷時には第８図のよ
うに３方弁２６、３６を切換える。Similarly, at low speed and high load, as shown in FIG.
6 is switched, and at the time of high speed and low load, 3-way valve 2 as shown in FIG.
6 and 36 are switched, and finally, at high speed and high load, the three-way valves 26 and 36 are switched as shown in FIG.
（発明の効果） 以上説明したように本発明による排気ターボ過給機付内
燃機関の排気ガス処理装置では、一方の高圧段排気ター
ボ過給機１６ｂのタービン１８ｂは、内燃機関の一部の
気筒用の排気マニホールド１４ｂに、一方の排気通路３
４を介して接続し、他方の高圧段排気ターボ過給機１６
ａのタービン１８ａは、残りの気筒用の排気マニホール
ド１４ａに他方の排気通路２４を介して接続し、両排気
通路２４，３４間にはこれらを接続する接続配管３８を
設け、一方の排気通路３４と接続配管３８との間に切替
自在な３方弁３６を介装し、他方の排気通路２４又は該
排気通路２４に他方のタービン１８ａを介して接続する
管路４０ａの途中に、排気ガスに熱量を追加するアフタ
ーバーナー装置２８および排気ガス浄化用の触媒３０を
設け、排気ガス量の少ない時に前記３方弁３６で排気ガ
スを他方の排気通路２４に繁がる高圧段排気ターボ過給
機１６ａだけに供給するようにしているので、排気ガス
量は少なく、かつディーゼルエンジン１０の燃焼状態が
悪い低速負荷時には、アフターバーナー装置２８、触媒
３０で排気ガスを浄化しながら、３方弁３６を切換えて
排気ガスを高圧段過給機１６ａのタービン１８ａに集中
されることができ、排気ガス量が少ないと効率が低下す
るタービン１８ａへの排気ガス供給量を増やして、ター
ビン１８ａのタービン効率を向上でき、ディーゼルエン
ジン１０の出力を増大することができる。(Effects of the Invention) As described above, in the exhaust gas treatment device for an internal combustion engine with an exhaust turbocharger according to the present invention, the turbine 18b of one high-pressure exhaust turbocharger 16b is a cylinder of a part of the internal combustion engine. Exhaust manifold 14b for one exhaust passage 3
4 and the other high pressure stage exhaust turbocharger 16
The turbine 18a of "a" is connected to the exhaust manifold 14a for the remaining cylinders via the other exhaust passage 24, and a connecting pipe 38 for connecting these is provided between the exhaust passages 24 and 34. A three-way valve 36 that is switchable between the exhaust gas and the connection pipe 38, and the exhaust gas is introduced into the other exhaust passage 24 or a conduit 40a connected to the exhaust passage 24 via the other turbine 18a. An afterburner device 28 for adding heat and an exhaust gas purifying catalyst 30 are provided, and when the exhaust gas amount is small, the three-way valve 36 causes the exhaust gas to proliferate in the other exhaust passage 24. Since the exhaust gas amount is small and the diesel engine 10 is in a poor combustion state at a low speed load, the afterburner device 28 and the catalyst 30 provide the exhaust gas. The exhaust gas can be concentrated on the turbine 18a of the high-pressure supercharger 16a by switching the three-way valve 36 while increasing the exhaust gas supply amount to the turbine 18a whose efficiency decreases when the exhaust gas amount is small. Thus, the turbine efficiency of the turbine 18a can be improved and the output of the diesel engine 10 can be increased.
第１図は本発明の第１実施例の低速低負荷時を示す構造
略図、第２図、第３図、第４図はそれぞれ別の作動状態
を示す第１実施例の構造略図、第５図は第２実施例の低
速低負荷時を示す構造略図、第６図、第７図、第８図は
それぞれ別の作動状態を示す第２実施例の構造略図であ
る。１０……ディーゼルエンジン、１６ａ、１６ｂ……
高圧段排気ターボ過給機、２０……低圧段排気ターボ過
給機、２６、３６……３方弁、２８……アフターバーナ
ー装置、３０……触媒FIG. 1 is a structural schematic diagram showing a first embodiment of the present invention at low speed and low load, and FIGS. 2, 3, and 4 are schematic structural diagrams of the first embodiment showing different operating states, respectively. FIG. 6 is a structural schematic diagram of the second embodiment at low speed and low load, and FIGS. 6, 7, and 8 are schematic structural diagrams of the second embodiment showing different operating states. 10 ... Diesel engine, 16a, 16b ...
High-pressure exhaust turbocharger, 20 ... Low-pressure exhaust turbocharger, 26, 36 ... 3-way valve, 28 ... Afterburner device, 30 ... Catalyst
───────────────────────────────────────────────────── フロントページの続き (72)発明者 高橋 透 大阪府大阪市北区茶屋町１番32号 ヤンマ ーディーゼル株式会社内 (56)参考文献 特開 昭59−203815（ＪＰ，Ａ) 特開 昭55−109726（ＪＰ，Ａ) 特開 昭47−43606（ＪＰ，Ａ) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Toru Takahashi 1-32 Chayamachi, Kita-ku, Osaka City, Osaka Prefecture Yanmar Diesel Co., Ltd. (56) References JP-A-59-203815 (JP, A) JP-A-SHO 55-109726 (JP, A) JP-A-47-43606 (JP, A)
Claims (1)
過給機と、１個の低圧段排気ターボ過給機とを設けた２
段過給機付内燃機関において、一方の高圧段排気ターボ
過給機(16b) のタービン(18b) は、内燃機関の一部の気
筒用の排気マニホールド(14b)に、一方の排気通路(34)
を介して接続し、他方の高圧段排気ターボ過給機(16a)
のタービン(18a) は、残りの気筒用の排気マニホールド
(14a )に他方の排気通路(24)を介して接続し、両排気通
路(24,34) 間にはこれらを接続する接続配管(38)を設
け、一方の排気通路(34)と接続配管(38)との間に切換自
在な３方弁(36)を介装し、他方の排気通路(24)又は該排
気通路(24)に他方のタービン(18a) を介して接続する管
路(40a) の途中に、排気ガスに熱量を追加するアフター
バーナー装置(28)および排気ガス浄化用の触媒(30)を設
け、排気ガス量の少ない時に前記３方弁(36)で排気ガス
を他方の排気通路(24)に繋がる高圧段排気ターボ過給機
(16a) だけに供給するようにしたことを特徴とする排気
ターボ過給機付内燃機関の排気ガス処理装置。1. A multi-cylinder internal combustion engine equipped with two high pressure exhaust turbochargers and one low pressure exhaust turbocharger.
In the internal combustion engine with a stage supercharger, the turbine (18b) of the high pressure stage exhaust turbocharger (16b) is connected to the exhaust manifold (14b) for one of the cylinders of the internal combustion engine. )
Via the other high pressure stage exhaust turbocharger (16a)
The turbine (18a) is the exhaust manifold for the remaining cylinders
(14a) via the other exhaust passage (24), and connecting pipes (38) connecting both exhaust passages (24, 34) to connect them to one exhaust passage (34). A switchable three-way valve (36) is interposed between the exhaust passage (24) and the other exhaust passage (24) or a pipe line connected to the exhaust passage (24) via the other turbine (18a). In the middle of 40a), an afterburner device (28) for adding heat quantity to the exhaust gas and a catalyst (30) for purifying the exhaust gas are provided. High pressure exhaust turbocharger connected to exhaust passage (24)
An exhaust gas treatment device for an internal combustion engine with an exhaust turbocharger, characterized in that it is supplied only to (16a).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62145673A JPH0647932B2 (en) | 1987-06-10 | 1987-06-10 | Exhaust gas treatment device for internal combustion engine with turbocharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62145673A JPH0647932B2 (en) | 1987-06-10 | 1987-06-10 | Exhaust gas treatment device for internal combustion engine with turbocharger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63309726A JPS63309726A (en) | 1988-12-16 |
| JPH0647932B2 true JPH0647932B2 (en) | 1994-06-22 |
Family
ID=15390440
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62145673A Expired - Lifetime JPH0647932B2 (en) | 1987-06-10 | 1987-06-10 | Exhaust gas treatment device for internal combustion engine with turbocharger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0647932B2 (en) |
Families Citing this family (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2832759B1 (en) * | 2001-11-29 | 2004-04-16 | Renault | DEVICE AND METHOD FOR SUPERCHARGING AN INTERNAL COMBUSTION ENGINE |
| DE10319594A1 (en) * | 2003-05-02 | 2004-11-18 | Daimlerchrysler Ag | Turbocharger device and a method for operating a turbocharger device |
| DE102004035325A1 (en) * | 2004-07-21 | 2006-02-16 | Bayerische Motoren Werke Ag | Exhaust gas aftertreatment with sequential charging |
| EP1640597B1 (en) * | 2004-09-22 | 2008-07-23 | Ford Global Technologies, LLC | Supercharged internal combustion engine and method for operating such an internal combustion engine |
| EP1728989B1 (en) * | 2005-05-31 | 2008-05-28 | BorgWarner Inc. | Multistage turbocharger arrangement |
| FR2892981B1 (en) * | 2005-11-09 | 2009-10-23 | Renault Sas | ENGINE EXHAUST DEVICE AND ENGINE |
| DE102007017845A1 (en) | 2007-04-16 | 2008-11-27 | Siemens Ag | Turbocharged internal combustion engine and method |
| ITBO20070352A1 (en) * | 2007-05-11 | 2008-11-12 | Ferrari Spa | TURBOCHARED INTERNAL COMBUSTION MOTOR WITH "V" ARRANGEMENT OF THE CYLINDERS |
| DE102007028493A1 (en) * | 2007-06-21 | 2008-12-24 | Robert Bosch Gmbh | Internal combustion engine with two-stage turbocharging and oxidation catalyst |
| CN102224074A (en) | 2008-09-23 | 2011-10-19 | 威罗门飞行公司 | Powerplant and related control system and method |
| DE102008043487A1 (en) * | 2008-11-05 | 2010-05-20 | Robert Bosch Gmbh | Internal combustion engine with turbocharger and oxidation catalyst |
| DE102008057572B4 (en) | 2008-11-15 | 2021-09-02 | Bayerische Motoren Werke Aktiengesellschaft | Exhaust system for an internal combustion engine |
| EP2372122B1 (en) * | 2008-12-26 | 2014-12-24 | Toyota Jidosha Kabushiki Kaisha | Exhaust purifying device for internal combustion engine with supercharger |
| FR2944560B1 (en) * | 2009-04-16 | 2011-04-01 | Inst Francais Du Petrole | DUAL-STAGE SUPER-POWER SYSTEM WITH EXHAUST GAS PURIFYING DEVICE FOR INTERNAL COMBUSTION ENGINE AND METHOD FOR CONTROLLING SUCH A SYSTEM |
| DE102010005814A1 (en) * | 2010-01-27 | 2011-07-28 | Bayerische Motoren Werke Aktiengesellschaft, 80809 | Exhaust gas system for internal combustion engine of passenger car, has exhaust manifold which is connected with exhaust tract in gas guiding manner, in which exhaust turbocharger is arranged |
| US10233756B2 (en) | 2013-08-27 | 2019-03-19 | Garrett Transportation I Inc. | Two-sided turbocharger wheel with differing blade parameters |
| GB201502010D0 (en) * | 2015-02-06 | 2015-03-25 | Jaguar Land Rover Ltd | A multi-stage exhaust turbocharger system |
| GB2534926B (en) * | 2015-02-06 | 2018-06-06 | Jaguar Land Rover Ltd | A multi-stage exhaust turbocharger system |
| CN106065809B (en) * | 2015-04-24 | 2020-12-25 | 福特环球技术公司 | Engine with two-stage supercharging and exhaust gas aftertreatment and method for operating the same |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55109726A (en) * | 1979-02-17 | 1980-08-23 | Kawasaki Heavy Ind Ltd | Method of and apparatus for cutting-off supercharger for diesel engine |
| JPS59203815A (en) * | 1983-05-04 | 1984-11-19 | Yanmar Diesel Engine Co Ltd | Treating device for exhaust gas from two-stage supercharging type internal-combustion engine |
-
1987
- 1987-06-10 JP JP62145673A patent/JPH0647932B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63309726A (en) | 1988-12-16 |
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