JPH0561445U - Exhaust gas recirculation system for internal combustion engine with supercharger - Google Patents
Exhaust gas recirculation system for internal combustion engine with superchargerInfo
- Publication number
- JPH0561445U JPH0561445U JP218792U JP218792U JPH0561445U JP H0561445 U JPH0561445 U JP H0561445U JP 218792 U JP218792 U JP 218792U JP 218792 U JP218792 U JP 218792U JP H0561445 U JPH0561445 U JP H0561445U
- Authority
- JP
- Japan
- Prior art keywords
- exhaust gas
- downstream
- gas recirculation
- intake
- supercharger
- 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.)
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- Exhaust-Gas Circulating Devices (AREA)
- Jet Pumps And Other Pumps (AREA)
Abstract
(57)【要約】
【目的】 過給機を備えるものにおいて、燃費を悪化さ
せることなく排気還流を良好に行わせる。
【構成】 コンプレッサタービン下流の吸気通路２３に
絞り部３３と円筒部３４と拡開部３５とを設けると共
に、拡開部３５の下流外周壁と絞り部３７とにより開口
部３８を下流に向けて形成する。また、円筒部３４外方
の中空部３６に排気還流通路３０の下流端を接続する。
(57) [Summary] [Purpose] To allow an exhaust gas recirculation to be performed well without deteriorating fuel efficiency in a vehicle equipped with a supercharger. [Structure] A throttle portion 33, a cylindrical portion 34, and a widening portion 35 are provided in an intake passage 23 downstream of a compressor turbine, and an opening 38 is directed downstream by a downstream outer peripheral wall of the widening portion 35 and a narrowing portion 37. Form. Further, the downstream end of the exhaust gas recirculation passage 30 is connected to the hollow portion 36 outside the cylindrical portion 34.
Description
【０００１】[0001]
本考案は、過給機付内燃機関の排気還流装置に関する。 The present invention relates to an exhaust gas recirculation device for an internal combustion engine with a supercharger.
【０００２】[0002]
過給機付内燃機関の排気還流装置の一従来例として、以下のようなものがある （特開昭５４−１９０１５号公報，実開昭５６−１０５６４６号公報，実開平２ −４３４４８号公報等参照）。 このものは、排気ターボ過給機のコンプレッサ下流の吸気通路に吸気絞り制御 弁を設けると共に、この吸気絞り制御弁下流の吸気通路と排気通路とを排気還流 通路により連通接続させている。また、排気還流通路に圧力動型の排気還流制御 弁を介装し、排気還流制御弁の作動室に前記吸気絞り制御弁下流の吸気圧力を導 入させている。 As a conventional example of an exhaust gas recirculation system for an internal combustion engine with a supercharger, there are the following ones (JP-A-54-19015, JP-A-56-105646, JP-A-2-43448, etc.). reference). In this system, an intake throttle control valve is provided in the intake passage downstream of the compressor of the exhaust turbocharger, and the intake passage downstream of the intake throttle control valve and the exhaust passage are connected by an exhaust gas recirculation passage. A pressure-controlled exhaust gas recirculation control valve is provided in the exhaust gas recirculation passage, and the intake pressure downstream of the intake throttle control valve is introduced into the working chamber of the exhaust gas recirculation control valve.
【０００３】 そして、所定運転領域において、前記吸気絞り制御弁により吸気を絞ることに より、排気還流制御弁を作動させて排気還流量を制御するようにしている。 また、排気還流装置の他の従来例として、図５に示すようなものがある（実公 昭５６−１１６４６号公報参照）。 このものは、ＬＰＧを燃料とする過給機を備えないエンジンであって、１次側 及び２次側絞弁１，２上流の吸気通路３にはＬＰＧ用ベンチュリ４が設けられ、 ベンチュリ４には連通孔５が多数形成されている。そして、ＬＰＧ燃焼はＬＰＧ 通路６及び計量オリフィス７を介してベンチュリ４の中空部に導入された後連通 孔５を介して吸気通路３に導入される。Then, in a predetermined operation region, the intake throttle control valve throttles intake air to operate the exhaust gas recirculation control valve to control the exhaust gas recirculation amount. Another example of the conventional exhaust gas recirculation device is shown in FIG. 5 (see Japanese Utility Model Publication No. 56-11646). This is an engine that does not include a supercharger that uses LPG as fuel. An LPG venturi 4 is provided in the intake passage 3 upstream of the primary side and secondary side throttle valves 1 and 2, and the venturi 4 is provided. Has a large number of communication holes 5. Then, the LPG combustion is introduced into the intake passage 3 via the rear communication hole 5 introduced into the hollow portion of the venturi 4 via the LPG passage 6 and the metering orifice 7.
【０００４】 また、ＬＰＧ用ベンチュリ４上流の吸気通路３には、ＥＧＲ用ベンチュリ８が 設けられ、ベンチュリ８には上流側及び下流側連通孔９，１０が形成されている 。そして、排気は、ＥＧＲ通路１１を介してベンチュリ８の中空部に導入された 後、主に下流側連通孔１０から吸気通路３に導入される。An EGR venturi 8 is provided in the intake passage 3 upstream of the LPG venturi 4, and the venturi 8 has upstream and downstream communication holes 9 and 10. Then, the exhaust gas is introduced into the hollow portion of the venturi 8 via the EGR passage 11, and then is mainly introduced into the intake passage 3 from the downstream side communication hole 10.
【０００５】[0005]
しかし、排気ターボ過給機のコンプレッサ下流に吸気絞り制御弁を備えると共 に前記制御弁下流の吸気通路に排気を還流する前者のものでは、吸気絞り制御弁 による圧力損失が大きくなるので、ポンピングロスが増大して燃費が悪化すると いう不具合がある。また、コンプレッサ下流に排気を還流すると、ディーゼルエ ンジンにおいては特に低速高負荷運転時に吸気圧力が排気圧力より高くなるので 、排気を還流できないという不具合がある。 However, in the former type in which the intake throttle control valve is provided downstream of the compressor of the exhaust turbocharger and the exhaust gas is recirculated to the intake passage downstream of the control valve, the pressure loss due to the intake throttle control valve becomes large, so pumping There is a problem that the loss increases and the fuel efficiency deteriorates. Further, when the exhaust gas is recirculated to the downstream side of the compressor, in the diesel engine, the intake pressure becomes higher than the exhaust pressure particularly during low-speed and high-load operation, so that the exhaust gas cannot be recirculated.
【０００６】 また、排気をＥＧＲ用ベンチュリ８の連通孔９，１０から吸気通路に導入する ものでは、前記と同様な不具合を有する他に、排気中の煤が特に連通孔１０に詰 まるという不具合がある。 逆に、排気をコンプレッサ上流に還流すると、排気中の煤がコンプレッサの翼 部に付着し作動不良の原因になるおそれがある。In addition, in the case of introducing the exhaust gas into the intake passage from the communication holes 9 and 10 of the EGR venturi 8, in addition to the same problem as described above, soot in the exhaust gas is particularly blocked in the communication hole 10. There is. On the contrary, if the exhaust gas is recirculated to the upstream side of the compressor, the soot in the exhaust gas may adhere to the blades of the compressor and cause malfunction.
【０００７】 本考案は、このような実状に鑑みてなされたもので、燃費を悪化させることな く排気還流を良好に行わせることを目的とする。The present invention has been made in view of such a situation, and an object thereof is to allow exhaust gas recirculation to be performed favorably without deteriorating fuel efficiency.
【０００８】[0008]
このため、本考案は過給機のコンプレッサタービン下流の吸気通路に、前記加 圧された吸気を絞る筒状の絞り部と、該絞り部下流端に接続される筒部と、を設 けると共に、前記絞り部及び筒部の外周方に吸気通路内壁とにより形成される中 空部を設け、前記筒部の最下流端外周壁との間に所定空隙の開口部を大略吸気通 路下流に向けて開口させて形成するべく前記筒部の最下流端外周壁に対向する突 出部を吸気通路に形成し、かつ前記中空部に排気還流通路の下流端部を連通接続 させるようにした。 Therefore, the present invention provides a tubular throttle portion that throttles the pressurized intake air and a tubular portion connected to the downstream end of the throttle portion in the intake passage downstream of the compressor turbine of the supercharger. A hollow portion formed by an inner wall of the intake passage is provided on the outer peripheral side of the throttle portion and the cylindrical portion, and an opening portion having a predetermined gap is provided between the outer peripheral wall of the cylindrical portion and the outermost peripheral end of the cylindrical portion substantially downstream of the intake passage. A projecting portion facing the outermost peripheral wall of the most downstream end of the tubular portion is formed in the intake passage so as to be opened toward the outside, and the downstream end portion of the exhaust gas recirculation passage is communicated with the hollow portion.
【０００９】[0009]
そして、加圧された吸気の流速を絞り部及び筒部にて速めて開口部内方を通過 する吸気の静圧を低下させ、その静圧により排気を開口部から吸気通路に吸引す るようにした。 Then, the flow velocity of the pressurized intake air is accelerated by the throttle and the cylinder to reduce the static pressure of the intake air passing through the inside of the opening, and the static pressure causes the exhaust gas to be sucked into the intake passage from the opening. did.
【００１０】[0010]
以下に、本考案の実施例を図面に基づいて説明する。 図１及び図２は本考案の一実施例を示す。 まず、排気ターボ過給機付ディーゼルエンジンの全体構成を図１に基づいて説 明すると、機関本体２１の吸気マニホールド２２には吸気通路を構成する吸気管 ２３が接続され、排気マニホールド２４には排気管２５が接続されている。前記 吸気管２３の途中には排気ターボ過給機２６のコンプレッサタービン２７が介装 され、排気管２５の途中には前記コンプレッサタービン２７を回転駆動する排気 タービン２８が介装されている。 An embodiment of the present invention will be described below with reference to the drawings. 1 and 2 show an embodiment of the present invention. First, the overall structure of the diesel engine with an exhaust turbocharger will be described with reference to FIG. 1. The intake manifold 22 of the engine body 21 is connected to an intake pipe 23 that constitutes an intake passage, and the exhaust manifold 24 is connected to the exhaust manifold 24. The pipe 25 is connected. A compressor turbine 27 of an exhaust turbocharger 26 is installed in the middle of the intake pipe 23, and an exhaust turbine 28 that rotates the compressor turbine 27 is installed in the middle of the exhaust pipe 25.
【００１１】 前記コンプレッサタービン２７下流の吸気管２３には後述の排気導入部２９が 形成され、この排気導入部２９と前記排気タービン２８上流の排気管２５とは排 気還流通路３０により連通接続されている。３１はエアクリーナ、３２はマフラ である。 前記排気導入部２９には図２に示すように円筒状の絞り部３３が上流側吸気管 ３の下流端部に同軸状に接続されて設けられ、絞り部３３は流路断面積が下流に なるに従って徐々に小さくなるように形成されている。前記絞り部３３の下流端 部には円筒状の細径部３４が同軸状に接続され、細径部３４の流路断面積が全域 に亘って略同様に形成されている。また、筒部３４の下流端部には円筒状の拡開 部３５が同軸状に接続され、拡開部３５は流路断面積が下流になるに従って徐々 に大きくなるように形成されている。An exhaust gas introducing portion 29, which will be described later, is formed in the intake pipe 23 downstream of the compressor turbine 27, and the exhaust gas introducing portion 29 and the exhaust pipe 25 upstream of the exhaust turbine 28 are connected to each other by an exhaust gas recirculation passage 30. ing. Reference numeral 31 is an air cleaner, and 32 is a muffler. As shown in FIG. 2, a cylindrical throttle portion 33 is coaxially connected to the downstream end portion of the upstream intake pipe 3 in the exhaust introduction portion 29, and the throttle portion 33 has a flow passage cross-sectional area downstream. It is formed so as to become gradually smaller. A cylindrical small-diameter portion 34 is coaxially connected to the downstream end of the narrowed portion 33, and the flow passage cross-sectional area of the small-diameter portion 34 is formed in substantially the same manner over the entire area. A cylindrical expansion portion 35 is coaxially connected to the downstream end of the cylindrical portion 34, and the expansion portion 35 is formed so that the cross-sectional area of the flow passage gradually increases toward the downstream side.
【００１２】 また、前記絞り部３３と細径部３４との外周を覆うように円筒状の中空部３６ が設けられ、中空部３６に前記排気還流通路３０が接続され、この中空部３６内 に排気還流通路３０から排気が導入される。前記中空部３６の下流端部には突出 部としての円筒状の絞り部３７が前記拡開部３５の外方を覆うように接続され、 絞り部３７は流路断面積が下流になるに従って徐々に小さくなるように形成され ている。ここで、絞り部３７内周壁と拡開部３５外周壁との間に、開口部３８が 下流に向かって開口して形成される。A cylindrical hollow portion 36 is provided so as to cover the outer circumferences of the throttle portion 33 and the small diameter portion 34, and the exhaust gas recirculation passage 30 is connected to the hollow portion 36. Exhaust gas is introduced from the exhaust gas recirculation passage 30. A cylindrical throttling portion 37 serving as a protruding portion is connected to the downstream end of the hollow portion 36 so as to cover the outside of the expanding portion 35, and the throttling portion 37 gradually becomes smaller as the flow passage cross-sectional area becomes downstream. It is formed to be small. Here, an opening 38 is formed between the inner peripheral wall of the narrowed portion 37 and the outer peripheral wall of the expanded portion 35 so as to open downstream.
【００１３】 また、前記絞り部３７下流端部には円筒状の細径部３９が同軸状に接続され、 細径部３９の流路断面積は全域に亘って略同様に形成されている。前記細径部３ ９の下流端部には拡開部４０が同軸状に接続され、拡開部４０の流路断面積は下 流になるに従って徐々に大きくなるように形成されている。前記拡開部４０の下 流端部には下流側の吸気管２３の上流端が同軸状に接続されている。Further, a cylindrical small-diameter portion 39 is coaxially connected to the downstream end of the throttle portion 37, and the flow passage cross-sectional area of the small-diameter portion 39 is formed to be substantially the same over the entire area. A widened portion 40 is coaxially connected to the downstream end of the small diameter portion 39, and the flow passage cross-sectional area of the widened portion 40 is formed so as to gradually increase as it flows downward. The upstream end of the downstream intake pipe 23 is coaxially connected to the downstream end of the expanding portion 40.
【００１４】 尚、４１は排気還流量を制御する排気還流制御弁である。 かかる構成によれば、コンプレッサタービン２７により加圧された吸気は、吸 気管２３を流通して絞り部３３，細径部３４に導入された後拡開部３５から細径 部３９に導入される。そして、絞り部３３，細径部３４において吸気の流速が速 められて静圧が低下した吸気が前記開口部３８内方を通過するので、エゼクタ効 果によって排気が開口部３８から通路内に吸引されて導入され吸気と混合される 。Reference numeral 41 is an exhaust gas recirculation control valve for controlling the amount of exhaust gas recirculation. According to this structure, the intake air pressurized by the compressor turbine 27 flows through the suction pipe 23 and is introduced into the throttle portion 33 and the small diameter portion 34, and is then introduced into the small diameter portion 39 from the expanded portion 35. .. Then, the flow velocity of the intake air is increased in the throttle portion 33 and the small diameter portion 34, and the intake air whose static pressure has decreased passes through the inside of the opening portion 38, so that the exhaust effect causes the exhaust gas to flow from the opening portion 38 into the passage. It is sucked in, introduced, and mixed with intake air.
【００１５】 このとき、吸気は絞り部３３，細径部３４をスムーズに流れるので、圧力損失 を従来例（吸気絞り制御弁を備えるもの）に較べて小さくできるため、ポンピン グロスを低減でき燃費を向上できる。特に、開口部３８が通路下流側に開口して いるので、排気の吸出効果を向上できる。また、前記静圧を充分に低くできるの で、過給圧力が排気圧力よりも高くても排気を吸気管２３内に導入でき排気還流 率を向上できる。また、開口部３８の流路断面積は比較的大きくなるので、排気 中の煤が開口部３８に詰まるのが防止できる。At this time, since the intake air smoothly flows through the throttle portion 33 and the small diameter portion 34, the pressure loss can be made smaller than that of the conventional example (the one having the intake throttle control valve), so that the pumping loss can be reduced and the fuel economy Can be improved. In particular, since the opening 38 opens to the downstream side of the passage, the exhaust gas suction effect can be improved. Further, since the static pressure can be made sufficiently low, the exhaust gas can be introduced into the intake pipe 23 and the exhaust gas recirculation rate can be improved even if the supercharging pressure is higher than the exhaust gas pressure. Further, since the flow passage cross-sectional area of the opening 38 is relatively large, it is possible to prevent the soot in the exhaust from clogging the opening 38.
【００１６】 図３は排気導入部２９の取付位置の変形例を示すものであり、コンプレッサタ ービン２７下流の吸気管２３にインタークーラ４２を備えるときには、インター クーラ４２下流の吸気管２３に排気導入部２９を設けるのが望ましい。 図４は排気導入部の変形例を示す。 本実施例は、吸気管５１内に絞り部５２と円筒部５３とを同軸状に設けると共 に、絞り部５２及び円筒部５３の外周に形成された中空部５４に排気還流通路５ ４の下流端部を連通接続する。FIG. 3 shows a modification of the mounting position of the exhaust introduction part 29. When the intake pipe 23 downstream of the compressor turbine 27 is provided with an intercooler 42, the exhaust introduction is carried out to the intake pipe 23 downstream of the intercooler 42. It is desirable to provide the portion 29. FIG. 4 shows a modification of the exhaust gas introducing portion. In this embodiment, the throttle portion 52 and the cylindrical portion 53 are coaxially provided in the intake pipe 51, and the exhaust gas recirculation passage 54 is provided in the hollow portion 54 formed on the outer periphery of the throttle portion 52 and the cylindrical portion 53. Connect the downstream ends in communication.
【００１７】 また、円筒部５３の最下流端外周壁との間に下流に開口する開口部５５を形成 させるべく、円筒状５３の最下流端部外壁と所定間隙を持たせて周状の突出部５ ６を吸気管５１内に形成する。 かかる構成のものは、吸気流速が小さいときに有効である。Further, in order to form an opening 55 that opens downstream between the outermost wall of the most downstream end of the cylindrical portion 53, a circumferential protrusion is formed with a predetermined gap with the outer wall of the most downstream end of the cylindrical portion 53. The part 56 is formed in the intake pipe 51. Such a structure is effective when the intake flow velocity is low.
【００１８】[0018]
本考案は、以上説明したように、過給機により加圧された吸気の流速を絞り部 及び筒部に速めて静圧を低下させその静圧により排気を効率良く開口部から吸引 するようにしたので、圧力損失を従来よりも低減でき燃費を向上できると共に排 気還流率を向上でき、また排気中の煤が開口部に詰まるのを防止できる。 As described above, the present invention accelerates the flow velocity of the intake air pressurized by the supercharger to the throttle portion and the cylinder portion to reduce the static pressure, and the static pressure sucks the exhaust gas efficiently from the opening. As a result, pressure loss can be reduced, fuel consumption can be improved, exhaust gas recirculation rate can be improved, and soot in exhaust gas can be prevented from clogging the opening.
【図１】本考案の一実施例を示す構成図。FIG. 1 is a configuration diagram showing an embodiment of the present invention.
【図２】同上の要部拡大図。FIG. 2 is an enlarged view of a main part of the above.
【図３】同上の変形例を示す図。FIG. 3 is a diagram showing a modified example of the above.
【図４】同上の他の変形例を示す図。FIG. 4 is a diagram showing another modification of the above.
【図５】排気還流装置の実施例を示す要部断面図。FIG. 5 is a sectional view of an essential part showing an embodiment of an exhaust gas recirculation device.
２３ 吸気管 ２６ 排気ターボ過給機 ２７ コンプレッサタービン ２９ 排気導入部 ３０ 排気還流通路 ３３ 絞り弁 ３４ 円筒部 ３５ 拡開部 ３６ 中空部 ３７ 絞り部 ３８ 開口部 23 Intake Pipe 26 Exhaust Turbocharger 27 Compressor Turbine 29 Exhaust Introducing Section 30 Exhaust Gas Recirculation Channel 33 Throttle Valve 34 Cylindrical Section 35 Expanding Section 36 Hollow Section 37 Throttling Section 38 Opening
Claims (1)
る過給機を備える過給機付内燃機関において、前記コン
プレッサタービン下流の吸気通路に、前記加圧された吸
気を絞る筒状の絞り部と、該絞り部下流部に接続される
筒部と、を設けると共に、前記絞り部及び筒部の外周方
に吸気通路内壁とにより形成される中空部を設け、前記
筒部の最下流端外周壁との間に所定空隙の開口部を大略
吸気通路下流に向けて開口させて形成するべく前記筒部
の最下流端外周壁に対向する突出部を吸気通路に形成
し、かつ前記中空部に排気還流通路の下流端部を連通接
続させたことを特徴とする過給機付内燃機関の排気還流
装置。1. An internal combustion engine with a supercharger comprising a supercharger for pressurizing intake air with a compressor turbine, and a tubular throttle portion for restricting the pressurized intake air in an intake passage downstream of the compressor turbine. A tubular portion connected to the downstream portion of the throttle portion, and a hollow portion formed by the intake passage inner wall on the outer peripheral side of the throttle portion and the tubular portion, and the outermost wall of the most downstream end of the tubular portion. A protrusion facing the outermost wall of the most downstream end of the tubular portion is formed in the intake passage to form an opening of a predetermined gap between the intake passage and the exhaust gas recirculation passage in the hollow portion. An exhaust gas recirculation system for an internal combustion engine with a supercharger, the downstream end of which is connected to communicate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP218792U JPH0561445U (en) | 1992-01-24 | 1992-01-24 | Exhaust gas recirculation system for internal combustion engine with supercharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP218792U JPH0561445U (en) | 1992-01-24 | 1992-01-24 | Exhaust gas recirculation system for internal combustion engine with supercharger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0561445U true JPH0561445U (en) | 1993-08-13 |
Family
ID=11522364
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP218792U Pending JPH0561445U (en) | 1992-01-24 | 1992-01-24 | Exhaust gas recirculation system for internal combustion engine with supercharger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0561445U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000249004A (en) * | 1999-03-02 | 2000-09-12 | Isuzu Motors Ltd | Egr device provided with reed valve |
| JP2001165002A (en) * | 1999-11-09 | 2001-06-19 | Caterpillar Inc | Intake venturi for exhaust gas circulating system in internal combustion engine |
| JP2006132373A (en) * | 2004-11-04 | 2006-05-25 | Hino Motors Ltd | Egr gas mixing device |
| JP2007092592A (en) * | 2005-09-28 | 2007-04-12 | Hino Motors Ltd | Egr gas mixing device |
| EP2236804A1 (en) * | 2009-03-31 | 2010-10-06 | Iveco S.p.A. | Gas mixing device particularly for internal-combustion engines equipped with exhaust gas recirculation system |
| JP2011112038A (en) * | 2009-11-30 | 2011-06-09 | Mitsubishi Heavy Ind Ltd | Egr device |
| JP2013083209A (en) * | 2011-10-11 | 2013-05-09 | Hino Motors Ltd | Egr gas mixer |
| US11591991B1 (en) * | 2021-08-27 | 2023-02-28 | Ford Global Technologies, Llc | Methods and systems for merging EGR with intake air |
-
1992
- 1992-01-24 JP JP218792U patent/JPH0561445U/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000249004A (en) * | 1999-03-02 | 2000-09-12 | Isuzu Motors Ltd | Egr device provided with reed valve |
| JP2001165002A (en) * | 1999-11-09 | 2001-06-19 | Caterpillar Inc | Intake venturi for exhaust gas circulating system in internal combustion engine |
| JP2006132373A (en) * | 2004-11-04 | 2006-05-25 | Hino Motors Ltd | Egr gas mixing device |
| JP2007092592A (en) * | 2005-09-28 | 2007-04-12 | Hino Motors Ltd | Egr gas mixing device |
| EP2236804A1 (en) * | 2009-03-31 | 2010-10-06 | Iveco S.p.A. | Gas mixing device particularly for internal-combustion engines equipped with exhaust gas recirculation system |
| JP2011112038A (en) * | 2009-11-30 | 2011-06-09 | Mitsubishi Heavy Ind Ltd | Egr device |
| JP2013083209A (en) * | 2011-10-11 | 2013-05-09 | Hino Motors Ltd | Egr gas mixer |
| US11591991B1 (en) * | 2021-08-27 | 2023-02-28 | Ford Global Technologies, Llc | Methods and systems for merging EGR with intake air |
| US20230064440A1 (en) * | 2021-08-27 | 2023-03-02 | Ford Global Technologies, Llc | Methods and systems for merging egr with intake air |
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