JP2522482Y2 - Exhaust gas recirculation structure of internal combustion engine with two-stage supercharger - Google Patents
Exhaust gas recirculation structure of internal combustion engine with two-stage superchargerInfo
- Publication number
- JP2522482Y2 JP2522482Y2 JP835092U JP835092U JP2522482Y2 JP 2522482 Y2 JP2522482 Y2 JP 2522482Y2 JP 835092 U JP835092 U JP 835092U JP 835092 U JP835092 U JP 835092U JP 2522482 Y2 JP2522482 Y2 JP 2522482Y2
- Authority
- JP
- Japan
- Prior art keywords
- exhaust gas
- stage
- exhaust
- pressure
- 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 - Fee Related
Links
Landscapes
- Supercharger (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本考案は、二段過給機を有する内
燃機関における排気ガスの再循環構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exhaust gas recirculation structure for an internal combustion engine having a two-stage supercharger.
【０００２】[0002]
【従来の技術】従来から内燃機関において、排気ガス中
の窒素酸化物等の有害物を低減するために、排気ガスを
再循環させて吸気中に還流し、エンジン内の燃焼を抑制
して窒素酸化物等の抑制を図る技術は、公知とされてい
るのである。即ち、エンジンの排気中に含まれる有害物
質、殊に、窒素酸化物を低減させる手段として、排気の
一部を吸気中に還流させるのである。この排気の吸気中
への還流は、吸気中に還流された排気がエンジンの燃焼
室内の燃焼を抑制し、その最高温度を下げて、窒素酸化
物の生成を低減するのである。しかし昨今では、環境問
題が大きく採り上げられ、より一層の排気ガス中の窒素
酸化物等の有害物質の除去が望まれるため、排気ガスの
再循環量、即ち、ＥＧＲ量をより多量にする技術が必要
となってきたのである。2. Description of the Related Art Conventionally, in an internal combustion engine, in order to reduce harmful substances such as nitrogen oxides in the exhaust gas, the exhaust gas is recirculated and returned to the intake air to suppress the combustion in the engine. Techniques for suppressing oxides and the like are known. That is, a part of the exhaust gas is recirculated into the intake air as a means for reducing harmful substances, particularly nitrogen oxides, contained in the exhaust gas of the engine. The recirculation of the exhaust gas into the intake air suppresses the combustion in the combustion chamber of the engine, and reduces the maximum temperature of the exhaust gas, thereby reducing the generation of nitrogen oxides. However, in recent years, environmental issues have been taken up greatly, and it is desired to further remove harmful substances such as nitrogen oxides in exhaust gas. Therefore, a technology for increasing the amount of exhaust gas recirculation, that is, the EGR amount, has been developed. It has become necessary.
【０００３】これに応える技術として、従来は、図２に
示す如き方法が用いられていた。即ち、エンジンＥは二
段過給機式となっており、吸気は、吸気管１ａより低圧
段（一段目）過給機の低圧段コンプレッサーＣ１、吸気
管１ｂ、高圧段（二段目）過給機の高圧段コンプレッサ
ーＣ２、さらに吸気管１ｃを経て、エンジンＥ内の燃焼
室に至るものである。なお、７は吸気冷却用のインター
クーラーである。エンジンＥは多気筒型であり（本図案
では６気筒型）、１〜３気筒の排気及び４〜６気筒の排
気は、高圧段（２段目）タービンＴ２の入口までの排気
管２ａ内においては中隔壁３によって仕切られて該高圧
段タービンＴ２に案内される。１〜３気筒及び４〜６気
筒の両側の排気が混じり合うと、乱気流を発生し、高圧
段タービンＴ２の効率が低下するので、中隔壁３を設け
ているのである。排気は、さらに排気管２ｂ、低圧段
（１段目）タービンＴ１を経て、排気管２ｃより排出さ
れるものである。As a technique for responding to this, conventionally, a method as shown in FIG. 2 has been used. That is, the engine E is of a two-stage supercharger type, and the intake air is supplied from the low-pressure stage (first stage) supercharger C1, the intake tube 1b, and the high-pressure stage (second stage) of the supercharger of the intake pipe 1a. The gas reaches the combustion chamber in the engine E via the high-pressure compressor C2 of the feeder and the intake pipe 1c. Reference numeral 7 denotes an intercooler for cooling the intake air. The engine E is a multi-cylinder type (six-cylinder type in the present design), and exhausts of the first to third cylinders and exhausts of the fourth to sixth cylinders are exhausted in an exhaust pipe 2a to an inlet of a high-pressure stage (second stage) turbine T2. Are partitioned by the partition wall 3 and guided to the high-pressure stage turbine T2. When the exhaust gas on both sides of the first to third cylinders and the fourth to sixth cylinders is mixed, turbulence is generated, and the efficiency of the high-pressure stage turbine T2 is reduced. Therefore, the inner partition wall 3 is provided. The exhaust gas is further discharged from the exhaust pipe 2c through the exhaust pipe 2b and the low-pressure stage (first stage) turbine T1.
【０００４】そこで、従来の図１の如き構成におけるＥ
ＧＲ技術は、低圧段タービンＴ１及び高圧段タービンＴ
２の両タービンからの排気を排出する排気管２ｃより、
低圧段（一段目）コンプレッサー入口側の吸気管１ａに
再循環路Ｒ’を設けるものである。該再循環路Ｒ’に
は、ＥＧＲ量調節バルブＶ１を設け、排気ガス中の黒煙
等除去用のフィルター４、冷却器５、及び気水分離器６
が配設されている。該再循環路の構成は、実開昭５８─
１８３９５４にて公知である。さらに、該排気管２ｃよ
り再循環路Ｒ’に背圧をかけるための排気出口バルブＶ
２を設けているのである。[0004] Therefore, E in the conventional configuration as shown in FIG.
The GR technology includes a low-pressure stage turbine T1 and a high-pressure stage turbine T
2 from an exhaust pipe 2c that discharges exhaust gas from both turbines.
A recirculation path R 'is provided in the intake pipe 1a on the low pressure stage (first stage) compressor inlet side. The recirculation path R ′ is provided with an EGR amount control valve V 1, a filter 4 for removing black smoke and the like in the exhaust gas, a cooler 5, and a steam separator 6.
Are arranged. The construction of the recirculation path is
183954. Further, an exhaust outlet valve V for applying back pressure from the exhaust pipe 2c to the recirculation path R '.
2 is provided.
【０００５】また、図２の如く、低圧段タービンからの
排気管から再循環路を設ける方法以外に、高圧側より低
圧側への排気の流れを利用して、該背圧をかけるバルブ
を不要とするために、実開平３─１２２２５９の如く、
高圧段タービン入口から排気の一部を抜き取る方法もあ
る。In addition to the method of providing a recirculation path from an exhaust pipe from a low pressure stage turbine as shown in FIG. 2, a valve for applying the back pressure by utilizing the flow of exhaust gas from a high pressure side to a low pressure side is unnecessary. In order to make
There is also a method of extracting a part of exhaust gas from the high pressure stage turbine inlet.
【０００６】[0006]
【考案が解決しようとする課題】図２の如き構成の排気
ガス再循環において問題となるのは、ＥＧＲ量調整バル
ブＶ１以外に排気出口バルブＶ２が必要であり、二つの
バルブ制御を行わなくてはならず、複雑な構造となって
いたのである。また、低公害化の要請から、該排気出口
バルブＶ２による背圧は相当高いものとしなければなら
ず、その背圧による排気抵抗で、エンジン性能の悪化を
ももたらしてしまうのである。The problem with the exhaust gas recirculation having the configuration shown in FIG. 2 is that an exhaust outlet valve V2 is required in addition to the EGR amount adjustment valve V1, and two valve controls are not performed. Instead, it had a complicated structure. In addition, due to the demand for low pollution, the back pressure by the exhaust outlet valve V2 must be considerably high, and the exhaust resistance due to the back pressure also causes deterioration of engine performance.
【０００７】また、高圧段タービン入口より排気の一部
を抜き取る方法は、図２の如く、多気筒型エンジンにお
いては、エンジンから高圧段タービンまでの排気管中に
構成している中隔壁３を一部削除しなければならず、そ
のため１〜３気筒側と４〜６気筒側の両排気が混じり合
って圧力バランスを崩し、該高圧段タービンの性能を劣
化させるのである。As shown in FIG. 2, a method of extracting a part of the exhaust gas from the inlet of the high-pressure stage turbine is as follows. Part of the exhaust has to be deleted, and therefore, the exhausts of the first to third cylinders and the fourth to sixth cylinders are mixed, and the pressure balance is lost, thereby deteriorating the performance of the high-pressure stage turbine.
【０００８】本考案は、図２図示の複雑なＥＧＲ制御を
要する構造を改善して、ＥＧＲ量調整バルブＶ１のみに
よる容易なＥＧＲ制御を行える如く再循環路を構成する
ものである。The present invention improves the structure requiring complicated EGR control shown in FIG. 2 and configures a recirculation path so that the EGR control can be easily performed only by the EGR amount adjustment valve V1.
【０００９】[0009]
【課題を解決するための手段】二段過給機を有する内燃
機関において、排気タービンの一段目過給機と二段目過
給機の間の排出ガスの一部を一段目コンプレッサーの吸
気口に再循環させる如く再循環路を構成するものであ
る。SUMMARY OF THE INVENTION In an internal combustion engine having a second-stage supercharger, part of exhaust gas between the first-stage supercharger and the second-stage supercharger of an exhaust turbine is supplied to an intake port of a first-stage compressor. A recirculation path is configured to recirculate the water.
【００１０】[0010]
【実施例】本考案の解決すべき課題及び構成は以上の如
くであり、次に添付の図面に示した本考案の実施例を説
明する。図１は本考案の２段過給器付エンジンＥにおけ
る排気ガス再循環の構造を示すシステム図、図２は従来
の２段過給器付エンジンＥの排気ガス再循環構造を示す
システム図である。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing the configuration of an embodiment of the present invention. FIG. 1 is a system diagram showing an exhaust gas recirculation structure in an engine E with a two-stage supercharger of the present invention, and FIG. 2 is a system diagram showing an exhaust gas recirculation structure of a conventional engine E with a two-stage supercharger. is there.
【００１１】図１の排気ガス再循環構造について説明す
る。本考案においては、高圧段（２段目）タービンＴ２
より低圧段（１段目）タービンＴ１までの排気管２ｂか
ら、低圧段（１段目）コンプレッサーＣ１の吸気口側の
吸気管１ａに至る再循環路Ｒを構成するものである。該
低圧段コンプレッサーＣ１により、新規の吸気を混合さ
れた上で、圧力を掛けた後に、インタークーラー７を通
過して、高圧段コンプレッサーＣ２に入り、更に加圧さ
れた状態で燃焼室に送りこまれるのである。そして該再
循環路ＲにＥＧＲ量調整バルブＶ１を介装している。そ
してＥＧＲ量調整バルブＶ１を介装した再循環路Ｒに
は、フィルター４と冷却器５と気水分離器６が介装され
ている。該フィルター４は排気ガス中の煤や塵埃を取り
去るものであり、また冷却器５は高温排気ガスを冷却す
るものである。また該高温排気ガスの冷却により、水蒸
気分が水滴に変わるので気水分離器６によりこの水滴を
分離すべく構成している。The exhaust gas recirculation structure shown in FIG. 1 will be described. In the present invention, the high-pressure stage (second stage) turbine T2
It constitutes a recirculation path R from the exhaust pipe 2b up to the lower pressure stage (first stage) turbine T1 to the intake pipe 1a on the intake port side of the low pressure stage (first stage) compressor C1. After the new intake air is mixed by the low-pressure stage compressor C1, after applying pressure, it passes through the intercooler 7, enters the high-pressure stage compressor C2, and is sent to the combustion chamber in a further pressurized state. is there. An EGR amount adjustment valve V1 is interposed in the recirculation path R. A filter 4, a cooler 5, and a water / water separator 6 are provided in the recirculation path R provided with the EGR amount adjustment valve V1. The filter 4 removes soot and dust in the exhaust gas, and the cooler 5 cools the high-temperature exhaust gas. The cooling of the high-temperature exhaust gas changes the water vapor into water droplets, so that the water / water separator 6 is configured to separate the water droplets.
【００１２】排気管２ｂにおいては、高圧段タービンＴ
２より低圧段タービンＴ１の間で、自然に排気に圧力が
掛かっているので、図２の従来技術の如き背圧をかける
バルブ（排気出口バルブＶ２）が必要なく、多量の排気
を再循環路Ｒに送り込む事ができ、制御面でもＥＧＲ量
調整バルブＶ１の制御のみで済むのである。また、高圧
段タービンの入口側より排気を取り入れる場合のよう
に、排気管２ａ中の中隔壁３を削除する必要もないので
ある。排気管２ａ中の中隔壁３を取り除く場合には、１
〜３気筒側と４〜６気筒側の両排気が混じり合って圧力
バランスを崩し、該高圧段タービンの性能を劣化させる
という不具合が発生するのであるが、この点を不具合を
解消することが出来るのである。しかも高圧段タービン
の入口側より排気を取り入れる場合に比べて本考案の方
が排気温度が低いため冷却器５の容量を小さくすること
ができる。なお、再循環路Ｒの途中の構成は、従来の如
く、フィルター４、冷却器５、及び気水分離器６を配設
するものである。また、ＥＧＲ量調整バルブＶ１は、電
磁バルブ等により構成される事が考えられるものであ
る。In the exhaust pipe 2b, a high-pressure stage turbine T
Since the pressure is naturally applied to the exhaust gas between the low pressure stage turbine T1 and T2, a valve (exhaust outlet valve V2) for applying a back pressure as in the prior art of FIG. Therefore, only the control of the EGR amount adjustment valve V1 is required in terms of control. Further, unlike the case where exhaust gas is taken in from the inlet side of the high-pressure stage turbine, there is no need to delete the inner partition wall 3 in the exhaust pipe 2a. When removing the inner partition wall 3 in the exhaust pipe 2a, 1
The exhaust of the three to four cylinders and the exhaust of the four to six cylinders are mixed, and the pressure balance is disturbed, and the performance of the high-pressure stage turbine is deteriorated. This problem can be solved. It is. In addition, since the exhaust temperature is lower in the present invention than in the case where exhaust gas is taken in from the inlet side of the high-pressure stage turbine, the capacity of the cooler 5 can be reduced. The configuration in the middle of the recirculation path R is such that the filter 4, the cooler 5, and the steam separator 6 are disposed as in the related art. Further, the EGR amount adjustment valve V1 may be constituted by an electromagnetic valve or the like.
【００１３】[0013]
【考案の効果】本考案は、以上のように構成する事によ
り、次のような効果を奏するものである。即ち、排気タ
ービンの一段目と二段目の間の排出ガスの一部を一段目
コンプレッサーの吸気口に再循環させる如くに再循環路
を構成した事により、背圧をかけることなく高圧の排気
を再循環路に送り込む事ができるので、多量のＥＧＲを
送り込む事が可能である。[Effects of the Invention] The present invention has the following effects by being configured as described above. In other words, by forming a recirculation path so as to recirculate part of the exhaust gas between the first and second stages of the exhaust turbine to the intake port of the first stage compressor, high-pressure exhaust without applying back pressure Can be sent to the recirculation path, so that a large amount of EGR can be sent.
【００１４】第２に、エンジン負荷の高低や回転数に応
じたＥＧＲ量の設定も、ＥＧＲ量調整バルブＶ１の一個
により制御する事ができるのである。また、高圧段ター
ビン入口側より排気ガスを抜く方法のように、排気圧の
バランスを崩してタービン性能を劣化させる恐れもない
のである。Second, the setting of the EGR amount according to the level of the engine load and the number of revolutions can be controlled by one EGR amount adjusting valve V1. Further, unlike the method of extracting exhaust gas from the inlet side of the high-pressure stage turbine, there is no possibility that the balance of the exhaust pressure is lost and the turbine performance is deteriorated.
【図１】本考案の２段過給器付エンジンＥにおける排気
ガス再循環の構造を示すシステム図である。FIG. 1 is a system diagram showing a structure of exhaust gas recirculation in an engine E with a two-stage supercharger of the present invention.
【図２】従来の２段過給器付エンジンＥにおける排気ガ
ス再循環構造を示すシステム図である。FIG. 2 is a system diagram showing an exhaust gas recirculation structure in a conventional engine E with a two-stage supercharger.
Ｅ エンジン Ｒ 排気ガス再循環路 Ｖ１ ＥＧＲ量調整バルブ Ｃ１ 低圧段コンプレッサー Ｃ２ 高圧段コンプレッサー Ｔ１ 低圧段タービン Ｔ２ 高圧段タービン １ａ，１ｂ，１ｃ 吸気管 ２ａ，２ｂ，２ｃ 排気管 ３ 中隔壁 E engine R exhaust gas recirculation path V1 EGR amount adjustment valve C1 low-pressure stage compressor C2 high-pressure stage compressor T1 low-pressure stage turbine T2 high-pressure stage turbine 1a, 1b, 1c Intake pipes 2a, 2b, 2c Exhaust pipe 3 Middle partition
Claims (1)
排気タービンの一段目過給機と二段目過給機の間の排気
ガスの一部を、一段目コンプレッサーの吸気口に再循環
させる事を特徴とする二段過給機付内燃機関の排気ガス
再循環構造。1. An internal combustion engine having a two-stage supercharger,
Exhaust of an internal combustion engine with a two-stage supercharger, characterized in that part of the exhaust gas between the first-stage supercharger and the second-stage supercharger of the exhaust turbine is recirculated to the intake port of the first-stage compressor. Gas recirculation structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP835092U JP2522482Y2 (en) | 1992-02-25 | 1992-02-25 | Exhaust gas recirculation structure of internal combustion engine with two-stage supercharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP835092U JP2522482Y2 (en) | 1992-02-25 | 1992-02-25 | Exhaust gas recirculation structure of internal combustion engine with two-stage supercharger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0569364U JPH0569364U (en) | 1993-09-21 |
| JP2522482Y2 true JP2522482Y2 (en) | 1997-01-16 |
Family
ID=11690779
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP835092U Expired - Fee Related JP2522482Y2 (en) | 1992-02-25 | 1992-02-25 | Exhaust gas recirculation structure of internal combustion engine with two-stage supercharger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2522482Y2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102004009794A1 (en) * | 2004-02-28 | 2005-09-22 | Daimlerchrysler Ag | Internal combustion engine with two exhaust gas turbochargers |
| JP4616707B2 (en) * | 2005-06-14 | 2011-01-19 | 日野自動車株式会社 | Exhaust gas recirculation structure for turbocharged engines |
| DE102007052899A1 (en) * | 2007-11-07 | 2009-05-14 | Ford Global Technologies, LLC, Dearborn | Charged internal combustion engine and method for operating such an internal combustion engine |
| KR101628548B1 (en) * | 2014-12-01 | 2016-06-09 | 현대자동차주식회사 | Apparatus of Two-stage turbo charger |
-
1992
- 1992-02-25 JP JP835092U patent/JP2522482Y2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0569364U (en) | 1993-09-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6981375B2 (en) | Turbocharged internal combustion engine with EGR flow | |
| KR101886090B1 (en) | Engine system | |
| JP4565605B2 (en) | Combustion engine with exhaust gas recirculation | |
| US6216459B1 (en) | Exhaust gas re-circulation arrangement | |
| US7941999B2 (en) | Internal combustion engine | |
| US7287378B2 (en) | Divided exhaust manifold system and method | |
| US6422222B1 (en) | Bi-turbocharger internal combustion engine with exhaust gas recycling | |
| US20080223038A1 (en) | Arrangement for Recirculating and Cooling Exhaust Gas of an Internal Combustion Engine | |
| US7584748B2 (en) | Exhaust gas recirculation system for an internal combustion engine | |
| US7448368B2 (en) | Exhaust gas recirculation system for an internal combustion engine | |
| CN100436770C (en) | Arrangement for controlling exhaust pressure pulses at an internal combustion engine | |
| JP2002188526A (en) | Egr device | |
| JPH09256915A (en) | Egr device for diesel engine with intercooler | |
| JPH0571426A (en) | Exhaust high pressurizing device for egr | |
| JP2522482Y2 (en) | Exhaust gas recirculation structure of internal combustion engine with two-stage supercharger | |
| JP3156414B2 (en) | Blow-by gas cooling device | |
| JP2002285879A (en) | Exhaust gas recirculation device for engine with supercharger | |
| US20210310446A1 (en) | Boosted engine | |
| JP4616707B2 (en) | Exhaust gas recirculation structure for turbocharged engines | |
| JP2000008963A (en) | Exhaust gas recirculation device for supercharged engine | |
| JP2005054710A (en) | Exhaust gas recirculation device for turbo compound engine | |
| JP2001355453A (en) | Intake air cooling device for internal combustion engine with supercharger | |
| JP4499961B2 (en) | Multi-cylinder supercharged engine | |
| JPH0458055A (en) | Exhaust gas recirculation device for diesel engine | |
| JP2004028052A (en) | Egr (exhaust gas recirculation) system of diesel engine with turbocharger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |