JP2013087720A - Venturi for egr - Google Patents
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- JP2013087720A JP2013087720A JP2011230651A JP2011230651A JP2013087720A JP 2013087720 A JP2013087720 A JP 2013087720A JP 2011230651 A JP2011230651 A JP 2011230651A JP 2011230651 A JP2011230651 A JP 2011230651A JP 2013087720 A JP2013087720 A JP 2013087720A
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- 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
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Abstract
Description
本発明は、エンジンの排気通路に接続されたＥＧＲ通路とエンジンの吸気通路との接続部に設けられるＥＧＲ用ベンチュリに関する。 The present invention relates to an EGR venturi provided at a connection portion between an EGR passage connected to an exhaust passage of an engine and an intake passage of the engine.
内燃機関（エンジン）において、ＮＯｘを低減させるためにＥＧＲ（排気再循環）システムが用いられる。図２にＥＧＲシステムの一例を示す。図２に示すＥＧＲシステムは、所謂高圧ＥＧＲシステムである。 In an internal combustion engine (engine), an EGR (exhaust gas recirculation) system is used to reduce NOx. FIG. 2 shows an example of the EGR system. The EGR system shown in FIG. 2 is a so-called high pressure EGR system.
図２に示すＥＧＲシステム５において、通常はターボチャージャ４のタービン４ａ入口圧力がターボチャージャ４のコンプレッサ４ｂ出口圧力よりも高いため、ＥＧＲバルブ５ｃを開くと、自然とＥＧＲが行われる。しかしながら、例えば大型ディーゼルエンジン（排気量１０Ｌ程度）では、コンプレッサ４ｂの効率が高いため、高負荷側では、コンプレッサ４ｂ出口圧力の方がタービン４ａ入口圧力よりも高くなってしまうことがある。 In the EGR system 5 shown in FIG. 2, since the inlet pressure of the turbine 4a of the turbocharger 4 is usually higher than the outlet pressure of the compressor 4b of the turbocharger 4, EGR is naturally performed when the EGR valve 5c is opened. However, for example, in a large diesel engine (displacement of about 10 L), the efficiency of the compressor 4b is high. Therefore, on the high load side, the compressor 4b outlet pressure may be higher than the turbine 4a inlet pressure.
そこで、図３に示すようなベンチュリ（ＥＧＲ用ベンチュリ）が用いられる。 Therefore, a venturi (EGR venturi) as shown in FIG. 3 is used.
図３に示すＥＧＲ用ベンチュリ３０は、インタークーラ９と吸気マニフォールド１ｃとの間の吸気管２（つまり、インタークーラ９よりも下流の吸気管２）に配設される。 The EGR venturi 30 shown in FIG. 3 is disposed in the intake pipe 2 (that is, the intake pipe 2 downstream of the intercooler 9) between the intercooler 9 and the intake manifold 1c.
図３に示すＥＧＲ用ベンチュリ３０は、吸気管２に設けられ、吸気管２の通路面積を絞るノズル部３１と、ノズル部３１よりも下流の吸気管２にノズル部３１と間隔を隔てて設けられ、吸気管２の下流側に行くに従い吸気管２の通路面積を増加させるディフューザ部３２と、ＥＧＲ管５ａに接続され、ノズル部３１とディフューザ部３２との間の間隙の外周に設けられる環状チャンバ３３を有するＥＧＲ合流部３４とを有する。 The EGR venturi 30 shown in FIG. 3 is provided in the intake pipe 2, and is provided in the intake pipe 2 downstream of the nozzle section 31 with a gap between the nozzle section 31 and the nozzle section 31 for reducing the passage area of the intake pipe 2. A diffuser portion 32 that increases the passage area of the intake pipe 2 as it goes downstream of the intake pipe 2, and an annular shape that is connected to the EGR pipe 5 a and provided at the outer periphery of the gap between the nozzle portion 31 and the diffuser portion 32. And an EGR junction 34 having a chamber 33.
図３に示すＥＧＲ用ベンチュリ３０では、ＥＧＲガスＧは吸気管２内における新気（吸気）Ｎの外周に吸い込まれるのみで、ＥＧＲガスＧと新気Ｎとの混合が促進されるわけではない。 In the EGR venturi 30 shown in FIG. 3, the EGR gas G is only sucked into the outer circumference of the fresh air (intake) N in the intake pipe 2, and the mixing of the EGR gas G and the fresh air N is not promoted. .
よって、多気筒エンジンであれば、気筒間でのＥＧＲガス量のバラツキが生じ得る。また、燃焼室内でのＥＧＲガスの偏在が生じ、燃焼室内でＮＯｘ発生も偏在し得る。これらの理由のため、ＮＯｘが狙い通りに低減しない可能性がある。 Therefore, in the case of a multi-cylinder engine, variations in the amount of EGR gas between cylinders may occur. In addition, EGR gas is unevenly distributed in the combustion chamber, and NOx generation may be unevenly distributed in the combustion chamber. For these reasons, NOx may not be reduced as intended.
そこで、本発明の目的は、ＥＧＲガスと新気とが良く混合されるＥＧＲ用ベンチュリを提供することにある。 Accordingly, an object of the present invention is to provide an EGR venturi in which EGR gas and fresh air are well mixed.
前記目的を達成するために、本発明は、エンジンの排気通路に接続されたＥＧＲ通路と前記エンジンの吸気通路との接続部に設けられるＥＧＲ用ベンチュリであって、前記吸気通路に設けられ、前記吸気通路の通路面積を絞るノズル部と、前記ノズル部よりも下流の前記吸気通路に前記ノズル部と間隔を隔てて設けられ、前記吸気通路の下流側に行くに従い前記吸気通路の通路面積を増加させるディフューザ部と、前記ＥＧＲ通路に接続され、前記ノズル部と前記ディフューザ部との間の間隙の外周に設けられる環状チャンバを有するＥＧＲ合流部と、前記ＥＧＲ合流部に設けられ、前記吸気通路に導入されるＥＧＲガスに旋回流を付与することにより前記吸気通路内におけるＥＧＲガスと新気との混合を促進するスワーラーとを備え、前記スワーラーは、前記ＥＧＲ合流部の周方向に間隔を隔てて複数設けられ、且つ、前記ＥＧＲ合流部の径方向に対して周方向に傾斜される羽根を有するものである。 To achieve the above object, the present invention provides an EGR venturi provided at a connection portion between an EGR passage connected to an exhaust passage of an engine and an intake passage of the engine, provided in the intake passage, A nozzle portion that restricts the passage area of the intake passage and the intake passage downstream from the nozzle portion are spaced from the nozzle portion, and the passage area of the intake passage increases toward the downstream side of the intake passage. A diffuser portion to be connected to the EGR passage, an EGR merging portion having an annular chamber provided on an outer periphery of a gap between the nozzle portion and the diffuser portion, and an EGR merging portion provided in the intake passage. A swirler that promotes mixing of EGR gas and fresh air in the intake passage by applying a swirling flow to the introduced EGR gas, Waller, a plurality are provided at intervals in the circumferential direction of the EGR confluence unit, and those having a blade which is inclined in the peripheral direction with respect to the radial direction of the EGR merging section.
前記羽根は、前記ＥＧＲ合流部における前記ノズル部と前記ディフューザ部との間の間隙により形成されるＥＧＲガス吸込口に配設されるものであっても良い。 The blade may be disposed in an EGR gas suction port formed by a gap between the nozzle portion and the diffuser portion in the EGR merging portion.
本発明によれば、ＥＧＲガスと新気とが良く混合されるＥＧＲ用ベンチュリを提供することができるという優れた効果を奏する。 According to the present invention, it is possible to provide an EGR venturi in which EGR gas and fresh air are well mixed.
以下、本発明の好適な実施形態を添付図面に基づいて詳述する。 DESCRIPTION OF EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.
図２に本実施形態に係るＥＧＲ用ベンチュリが用いられるＥＧＲシステムを示す。 FIG. 2 shows an EGR system in which the EGR venturi according to this embodiment is used.
図２に示すように、エンジン１は、エンジン本体１ａと、エンジン本体１ａに吸気を供給する吸気通路（吸気管）２と、エンジン本体１ａからの排気を排出する排気通路（排気管）３と、エンジン本体１ａに供給する吸気を昇圧するためのターボチャージャ４と、排気通路３の排気の一部を吸気通路２に戻すＥＧＲシステム５とを備える。 As shown in FIG. 2, the engine 1 includes an engine body 1a, an intake passage (intake pipe) 2 that supplies intake air to the engine body 1a, and an exhaust passage (exhaust pipe) 3 that discharges exhaust from the engine body 1a. A turbocharger 4 for boosting the intake air supplied to the engine body 1a and an EGR system 5 for returning a part of the exhaust gas in the exhaust passage 3 to the intake passage 2 are provided.
エンジン１は、エンジン本体１ａに複数の気筒（燃焼室）１ｂが形成された多気筒エンジン（本実施形態では、多気筒ディーゼルエンジン）であり、気筒１ｂに、吸気通路２の下流端をなす吸気マニフォールド１ｃと、排気通路３の上流端をなす排気マニフォールド１ｄとが接続される。なお、図２ではエンジン本体１ａの一気筒のみを示している。 The engine 1 is a multi-cylinder engine (in this embodiment, a multi-cylinder diesel engine) in which a plurality of cylinders (combustion chambers) 1b are formed in an engine body 1a, and intake air that forms the downstream end of an intake passage 2 in the cylinder 1b. The manifold 1c and the exhaust manifold 1d forming the upstream end of the exhaust passage 3 are connected. FIG. 2 shows only one cylinder of the engine body 1a.
ターボチャージャ４は、排気管３に配設されたタービン４ａと、吸気管２に配設されたコンプレッサ４ｂとを有する。タービン４ａよりも下流の排気管３には、排気ブレーキバルブ６及びマフラー７等が設けられる。コンプレッサ４ｂよりも上流の吸気管２にはエアクリーナ８が設けられ、コンプレッサ４ｂよりも下流の吸気管２にはインタークーラ９が設けられる。 The turbocharger 4 includes a turbine 4 a disposed in the exhaust pipe 3 and a compressor 4 b disposed in the intake pipe 2. An exhaust brake valve 6 and a muffler 7 are provided in the exhaust pipe 3 downstream of the turbine 4a. An air cleaner 8 is provided in the intake pipe 2 upstream of the compressor 4b, and an intercooler 9 is provided in the intake pipe 2 downstream of the compressor 4b.
ＥＧＲシステム５は、所謂高圧ＥＧＲシステムであり、タービン４ａよりも上流の排気管３とコンプレッサ４ｂよりも下流の吸気管２とを連通するＥＧＲ通路（ＥＧＲ管）５ａと、ＥＧＲ管５ａに設けられたＥＧＲクーラ５ｂと、ＥＧＲクーラ５ｂよりも下流のＥＧＲ管５ａに設けられたＥＧＲバルブ５ｃとを有する。 The EGR system 5 is a so-called high pressure EGR system, and is provided in an EGR passage (EGR pipe) 5a that connects the exhaust pipe 3 upstream of the turbine 4a and the intake pipe 2 downstream of the compressor 4b, and the EGR pipe 5a. The EGR cooler 5b and the EGR valve 5c provided in the EGR pipe 5a downstream of the EGR cooler 5b.
図２に示すＥＧＲシステム５では、ＥＧＲ用ベンチュリ１０は、ＥＧＲ管５ａと吸気管２との接続部に配設される。より詳細には、ＥＧＲ用ベンチュリ１０は、インタークーラ９と吸気マニフォールド１ｃとの間の吸気管２（つまり、インタークーラ９よりも下流の吸気管２）に配設される。 In the EGR system 5 shown in FIG. 2, the EGR venturi 10 is disposed at a connection portion between the EGR pipe 5 a and the intake pipe 2. More specifically, the EGR venturi 10 is disposed in the intake pipe 2 between the intercooler 9 and the intake manifold 1c (that is, the intake pipe 2 downstream of the intercooler 9).
図１に本実施形態に係るＥＧＲ用ベンチュリを示す。 FIG. 1 shows an EGR venturi according to this embodiment.
図１に示すように、本実施形態に係るＥＧＲ用ベンチュリ１０は、吸気管２に設けられ、吸気管２の通路面積を絞るノズル部１１と、ノズル部１１よりも下流の吸気管２にノズル部１１と間隔を隔てて設けられ、吸気管２の下流側に行くに従い吸気管２の通路面積を増加させるディフューザ部１２と、ＥＧＲ管５ａに接続され、ノズル部１１とディフューザ部１２との間の間隙の外周に設けられる環状チャンバ１３を有するＥＧＲ合流部１４と、ＥＧＲ合流部１４に設けられ、吸気管２に導入されるＥＧＲガスに旋回流を付与するスワーラー１５とを備える。 As shown in FIG. 1, an EGR venturi 10 according to the present embodiment is provided in an intake pipe 2, and a nozzle portion 11 that narrows the passage area of the intake pipe 2 and a nozzle in the intake pipe 2 downstream of the nozzle portion 11. The diffuser part 12 is provided at a distance from the part 11 and increases the passage area of the intake pipe 2 toward the downstream side of the intake pipe 2, and is connected to the EGR pipe 5 a and between the nozzle part 11 and the diffuser part 12. And an EGR merging portion 14 having an annular chamber 13 provided on the outer periphery of the gap, and a swirler 15 provided in the EGR merging portion 14 and imparting a swirling flow to the EGR gas introduced into the intake pipe 2.
ノズル部１１は、吸気管２の下流側に行くに従い吸気管２の通路面積を面積Ａから面積Ａ1まで減少させることにより、吸気管２の通路面積を絞るものである。なお、図例では、ノズル部１１は、吸気管２の通路面積を比較的短い距離で面積Ａから面積Ａ1まで減少させているが、吸気管２の通路面積をより長い距離で面積Ａから面積Ａ1まで順次減少させるものであっても良い。 The nozzle portion 11 narrows the passage area of the intake pipe 2 by decreasing the passage area of the intake pipe 2 from the area A to the area A 1 as it goes downstream of the intake pipe 2. In the illustrated example, the nozzle section 11 reduces the passage area of the intake pipe 2 from the area A to the area A 1 at a relatively short distance, but the passage area of the intake pipe 2 is increased from the area A at a longer distance. or it may be of sequentially reduced to area A 1.
ディフューザ部１２は、吸気管２の下流側に行くに従い吸気管２の通路面積を面積Ａ1よりも小さい面積Ａ2（不図示）（Ａ2＜Ａ1）から面積Ａまで順次増加させるものである。また、ディフューザ部１２は、ノズル部１１に対して同心的に配設される。 The diffuser portion 12 increases the passage area of the intake pipe 2 from an area A 2 (not shown) (A 2 <A 1 ) smaller than the area A 1 to an area A as it goes downstream of the intake pipe 2. is there. Further, the diffuser portion 12 is disposed concentrically with the nozzle portion 11.
ＥＧＲ合流部１４は、ノズル部１１の下流端及びディフューザ部１２の上流端を覆うように設けられるものである。即ち、ＥＧＲ合流部１４内に環状チャンバ１３が区画形成される。また、ＥＧＲ合流部１４には、ＥＧＲ管５ａの下流端が接続される。 The EGR merge portion 14 is provided so as to cover the downstream end of the nozzle portion 11 and the upstream end of the diffuser portion 12. That is, the annular chamber 13 is defined in the EGR junction 14. Further, the downstream end of the EGR pipe 5a is connected to the EGR junction 14.
スワーラー１５は、ＥＧＲ合流部１４（環状チャンバ１３）の周方向に間隔を隔てて複数設けられ、且つ、ＥＧＲ合流部１４の径方向に対して周方向に傾斜される羽根（フィン）１６を有する。 The swirler 15 includes a plurality of blades (fins) 16 that are provided at intervals in the circumferential direction of the EGR merging portion 14 (annular chamber 13) and are inclined in the circumferential direction with respect to the radial direction of the EGR merging portion 14. .
より詳細には、羽根１６は、ノズル部１１の下流端とディフューザ部１２の上流端との間の間隙により形成される、ＥＧＲ合流部１４のＥＧＲガス吸込口（環状スリット）１７に配設される。また、羽根１６は、ＥＧＲガス吸込口１７から環状チャンバ１３内まで延びている。 More specifically, the blade 16 is disposed in an EGR gas suction port (annular slit) 17 of the EGR merging portion 14 formed by a gap between the downstream end of the nozzle portion 11 and the upstream end of the diffuser portion 12. The Further, the blade 16 extends from the EGR gas suction port 17 into the annular chamber 13.
また、図例では、羽根１６をＥＧＲ合流部１４の周方向に等間隔で８枚設けると共に、各羽根１６をＥＧＲ合流部１４の径方向に対して４５°だけ周方向に傾斜させている。なお、羽根１６の枚数、配置間隔及び傾斜角度は図例のものには限定されない。 In the illustrated example, eight blades 16 are provided at equal intervals in the circumferential direction of the EGR merging portion 14, and each blade 16 is inclined in the circumferential direction by 45 ° with respect to the radial direction of the EGR merging portion 14. In addition, the number of blades 16, the arrangement interval, and the inclination angle are not limited to those illustrated.
ノズル部１１、ディフューザ部１２、ＥＧＲ合流部１４及び羽根１６は、例えば鋳造等により一体成形されるのが好ましい。なお、ノズル部１１、ディフューザ部１２、ＥＧＲ合流部１４及び羽根１６の一部又は全部を、別体としても設けても良いのは勿論である。 The nozzle portion 11, the diffuser portion 12, the EGR merging portion 14, and the blades 16 are preferably integrally formed by casting or the like, for example. Of course, a part or all of the nozzle part 11, the diffuser part 12, the EGR merging part 14, and the blades 16 may be provided as separate bodies.
次に、本実施形態の作用を説明する。 Next, the operation of this embodiment will be described.
本実施形態に係るＥＧＲ用ベンチュリ１０では、ＥＧＲ合流部１４のＥＧＲガス吸込口１７に、斜めの羽根１６を有するスワーラー１５を設けている。ＥＧＲ合流部１４にスワーラー１５を設けることにより、ＥＧＲ合流部１４（環状チャンバ１３）からのＥＧＲガスＧは、吸気管２の周方向に対する旋回流を付与された状態で吸気管２に導入される。そして、ＥＧＲガスＧの旋回流により吸気管２内の新気Ｎにも旋回流が付与されると共に、新気ＮとＥＧＲガスＧとの比重差（新気Ｎの温度は通常ＥＧＲガスＧの温度よりも低いため、新気ＮはＥＧＲガスＧよりも重い）により、新気Ｎには吸気管２内を外周側へと向かう流れも生じる。そのため、吸気管２内におけるＥＧＲガスＧと新気Ｎとの混合が促進されて、吸気マニフォールド１ｃに至るまでにＥＧＲガスＧと新気Ｎとが良く混合される。 In the EGR venturi 10 according to the present embodiment, a swirler 15 having oblique blades 16 is provided at the EGR gas suction port 17 of the EGR merging portion 14. By providing the swirler 15 in the EGR merging portion 14, the EGR gas G from the EGR merging portion 14 (annular chamber 13) is introduced into the intake pipe 2 in a state where a swirling flow in the circumferential direction of the intake pipe 2 is applied. . Then, the swirl flow of the EGR gas G also imparts a swirl flow to the fresh air N in the intake pipe 2, and the specific gravity difference between the fresh air N and the EGR gas G (the temperature of the fresh air N is normally equal to that of the EGR gas G). Since the temperature is lower than the temperature, the fresh air N is heavier than the EGR gas G), so that the fresh air N also flows toward the outer peripheral side in the intake pipe 2. Therefore, mixing of the EGR gas G and the fresh air N in the intake pipe 2 is promoted, and the EGR gas G and the fresh air N are well mixed before reaching the intake manifold 1c.
また、ＥＧＲ用ベンチュリ１０にてＥＧＲガスと新気とが良く混合されるので、ＥＧＲガス量の気筒間バラツキ、燃焼室内でのＥＧＲガスの偏在を抑制することができる。よって、ＮＯｘを狙い通りに低減させることができる。 Further, since the EGR gas and the fresh air are well mixed in the EGR venturi 10, it is possible to suppress the variation in the amount of EGR gas between the cylinders and the uneven distribution of the EGR gas in the combustion chamber. Therefore, NOx can be reduced as intended.
以上要するに、本実施形態によれば、ＥＧＲガスと新気とが良く混合されるＥＧＲ用ベンチュリ１０を提供することが可能となる。 In short, according to the present embodiment, it is possible to provide the EGR venturi 10 in which EGR gas and fresh air are well mixed.
以上、本発明の好適な実施形態について説明したが、本発明は上述の実施形態には限定されず他の様々な実施形態を採ることが可能である。 The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various other embodiments can be adopted.
例えば、エンジン１は、ディーゼルエンジンには限定はされず、例えばガソリンエンジン等であっても良い。 For example, the engine 1 is not limited to a diesel engine, and may be, for example, a gasoline engine.
１ 内燃機関（エンジン）
２ 吸気管（吸気通路）
３ 排気管（排気通路）
５ ＥＧＲシステム
５ａ ＥＧＲ管（ＥＧＲ通路）
１０ ＥＧＲ用ベンチュリ
１１ ノズル部
１２ ディフューザ部
１３ 環状チャンバ
１４ ＥＧＲ合流部
１５ スワーラー
１６ 羽根
１７ ＥＧＲガス吸込口
1 Internal combustion engine
2 Intake pipe (intake passage)
3 Exhaust pipe (exhaust passage)
5 EGR system 5a EGR pipe (EGR passage)
10 EGR Venturi 11 Nozzle Part 12 Diffuser Part 13 Annular Chamber 14 EGR Merging Part 15 Swirler 16 Blade 17 EGR Gas Suction Port
Claims (2)
前記吸気通路に設けられ、前記吸気通路の通路面積を絞るノズル部と、前記ノズル部よりも下流の前記吸気通路に前記ノズル部と間隔を隔てて設けられ、前記吸気通路の下流側に行くに従い前記吸気通路の通路面積を増加させるディフューザ部と、前記ＥＧＲ通路に接続され、前記ノズル部と前記ディフューザ部との間の間隙の外周に設けられる環状チャンバを有するＥＧＲ合流部と、前記ＥＧＲ合流部に設けられ、前記吸気通路に導入されるＥＧＲガスに旋回流を付与することにより前記吸気通路内におけるＥＧＲガスと新気との混合を促進するスワーラーとを備え、
前記スワーラーは、前記ＥＧＲ合流部の周方向に間隔を隔てて複数設けられ、且つ、前記ＥＧＲ合流部の径方向に対して周方向に傾斜される羽根を有することを特徴とするＥＧＲ用ベンチュリ。 An EGR venturi provided at a connection portion between an EGR passage connected to an exhaust passage of the engine and an intake passage of the engine,
A nozzle portion that is provided in the intake passage and narrows the passage area of the intake passage, and is provided in the intake passage downstream from the nozzle portion with a gap from the nozzle portion, and as it goes downstream of the intake passage. A diffuser portion that increases a passage area of the intake passage; an EGR merging portion that is connected to the EGR passage and has an annular chamber provided on an outer periphery of a gap between the nozzle portion and the diffuser portion; and the EGR merging portion A swirler that promotes mixing of EGR gas and fresh air in the intake passage by imparting a swirling flow to the EGR gas introduced into the intake passage,
The swirler includes a plurality of swirlers spaced apart in the circumferential direction of the EGR merging portion and having blades inclined in the circumferential direction with respect to the radial direction of the EGR merging portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011230651A JP2013087720A (en) | 2011-10-20 | 2011-10-20 | Venturi for egr |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011230651A JP2013087720A (en) | 2011-10-20 | 2011-10-20 | Venturi for egr |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2013087720A true JP2013087720A (en) | 2013-05-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2011230651A Pending JP2013087720A (en) | 2011-10-20 | 2011-10-20 | Venturi for egr |
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| JP (1) | JP2013087720A (en) |
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| US20120180478A1 (en) * | 2011-01-18 | 2012-07-19 | GM Global Technology Operations LLC | Exhaust gas recirculation system for an internal combustion engine |
| CN103397959A (en) * | 2013-07-02 | 2013-11-20 | 广西玉柴机器股份有限公司 | Air inlet connecting pipe of EGR engine |
| JP2015010567A (en) * | 2013-07-01 | 2015-01-19 | 日野自動車株式会社 | Egr gas mixer |
| KR101541959B1 (en) * | 2013-08-14 | 2015-08-12 | 한준희 | Ozone contact water purification device |
| CN105626321A (en) * | 2016-03-22 | 2016-06-01 | 奇瑞汽车股份有限公司 | EGR mixer of gasoline engine |
| WO2017034548A1 (en) * | 2015-08-25 | 2017-03-02 | Borgwarner Inc. | Mixing device and method of making and using the same |
| US10316803B2 (en) | 2017-09-25 | 2019-06-11 | Woodward, Inc. | Passive pumping for recirculating exhaust gas |
| WO2019127098A1 (en) * | 2017-12-27 | 2019-07-04 | 潍柴动力股份有限公司 | Engine and mixed-gas intake device thereof |
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| US10995705B2 (en) | 2019-02-07 | 2021-05-04 | Woodward, Inc. | Modular exhaust gas recirculation system |
| US11174809B1 (en) | 2020-12-15 | 2021-11-16 | Woodward, Inc. | Controlling an internal combustion engine system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US8689553B2 (en) * | 2011-01-18 | 2014-04-08 | GM Global Technology Operations LLC | Exhaust gas recirculation system for an internal combustion engine |
| US20120180478A1 (en) * | 2011-01-18 | 2012-07-19 | GM Global Technology Operations LLC | Exhaust gas recirculation system for an internal combustion engine |
| JP2015010567A (en) * | 2013-07-01 | 2015-01-19 | 日野自動車株式会社 | Egr gas mixer |
| CN103397959A (en) * | 2013-07-02 | 2013-11-20 | 广西玉柴机器股份有限公司 | Air inlet connecting pipe of EGR engine |
| KR101541959B1 (en) * | 2013-08-14 | 2015-08-12 | 한준희 | Ozone contact water purification device |
| WO2017034548A1 (en) * | 2015-08-25 | 2017-03-02 | Borgwarner Inc. | Mixing device and method of making and using the same |
| CN105626321A (en) * | 2016-03-22 | 2016-06-01 | 奇瑞汽车股份有限公司 | EGR mixer of gasoline engine |
| US10634099B2 (en) | 2017-09-25 | 2020-04-28 | Woodward, Inc. | Passive pumping for recirculating exhaust gas |
| US10316803B2 (en) | 2017-09-25 | 2019-06-11 | Woodward, Inc. | Passive pumping for recirculating exhaust gas |
| WO2019127098A1 (en) * | 2017-12-27 | 2019-07-04 | 潍柴动力股份有限公司 | Engine and mixed-gas intake device thereof |
| US11002227B2 (en) | 2017-12-27 | 2021-05-11 | Weichai Power Co., Ltd. | Engine and mixed-gas intake device thereof |
| US10995705B2 (en) | 2019-02-07 | 2021-05-04 | Woodward, Inc. | Modular exhaust gas recirculation system |
| CN112628033A (en) * | 2019-09-24 | 2021-04-09 | 上海汽车集团股份有限公司 | Condensed water separation component, mixer with same and EGR system |
| CN112628033B (en) * | 2019-09-24 | 2022-04-22 | 上海汽车集团股份有限公司 | Condensed water separation component, mixer with same and EGR system |
| US11293382B2 (en) | 2020-01-08 | 2022-04-05 | Woodward, Inc. | Passive pumping for recirculating exhaust gas |
| US11174809B1 (en) | 2020-12-15 | 2021-11-16 | Woodward, Inc. | Controlling an internal combustion engine system |
| US11215132B1 (en) | 2020-12-15 | 2022-01-04 | Woodward, Inc. | Controlling an internal combustion engine system |
| 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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