JP2013525685A - Exhaust gas turbocharger compressor - Google Patents
Exhaust gas turbocharger compressor Download PDFInfo
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- JP2013525685A JP2013525685A JP2013508040A JP2013508040A JP2013525685A JP 2013525685 A JP2013525685 A JP 2013525685A JP 2013508040 A JP2013508040 A JP 2013508040A JP 2013508040 A JP2013508040 A JP 2013508040A JP 2013525685 A JP2013525685 A JP 2013525685A
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- compressor
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- exhaust gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D9/00—Stators
- F01D9/06—Fluid supply conduits to nozzles or the like
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- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
-
- 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
- F01N1/00—Silencing apparatus characterised by method of silencing
- F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
- F01N1/165—Silencing apparatus characterised by method of silencing by using movable parts for adjusting flow area
-
- 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
-
- 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
- F02B37/16—Control of the pumps by bypassing charging air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
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- 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
- F02B2037/125—Control for avoiding pump stall or surge
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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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Supercharger (AREA)
Abstract
本発明は、排気ガスターボチャージャ（１）のコンプレッサ（８）であって、コンプレッサホイール回転方向（ＶＲ）に駆動することができるコンプレッサホイール（１１）を有し、流入空気の流れ方向に見たときに、コンプレッサホイール（１１）が好ましくは管状のコンプレッサ入口（１２）とコンプレッサ出口（１３）との間に配置されるコンプレッサハウジング（１０）を有し、コンプレッサハウジング（１０）内でコンプレッサ出口（１３）からコンプレッサ入口（１２）に進行するオーバーラン空気再循環弁の流入ダクト（１４、１５）を有し、流入ダクト（１４、１５）が、前記コンプレッサ入口（１２）の内径（Ｄｉ）に対してほぼ円周方向にコンプレッサ入口（１２）に通じるコンプレッサ（８）に関する。 The present invention is a compressor (8) of an exhaust gas turbocharger (1), which has a compressor wheel (11) that can be driven in the direction of rotation of the compressor wheel (VR), and is viewed in the flow direction of the incoming air. Sometimes, the compressor wheel (11) has a compressor housing (10), preferably disposed between the tubular compressor inlet (12) and the compressor outlet (13), and the compressor outlet ( 13) has an inflow duct (14, 15) of an overrun air recirculation valve that advances from the compressor inlet (12), and the inflow duct (14, 15) has an inner diameter (Di) of the compressor inlet (12). On the other hand, it relates to the compressor (8) leading to the compressor inlet (12) in a substantially circumferential direction.
Description
本発明は、請求項１の前段に記載の排気ガスターボチャージャのコンプレッサに関する。 The present invention relates to an exhaust gas turbocharger compressor according to the preceding stage of claim 1.
オーバーラン空気再循環弁が設けられる一般的なコンプレッサでは、コンプレッサハウジングは、コンプレッサ出口からコンプレッサ入口に進行する流入ダクトを有する。前記流入ダクトは、排気ガスターボチャージャの動作中にポンピング効果を防止するためにオーバーラン空気再循環弁によって制御され、ポンピング効果は、例えば、自動車の制動工程のために絞りフラップが閉じられるが、排気ガスターボチャージャが依然として高い回転速度で動くであろう場合に発生する可能性がある。この状況で、上記の効果を防止するためには、オーバーラン空気再循環弁が開かれ、空気がコンプレッサ出口、または圧力側からコンプレッサ入口に導かれ、それにより大きな圧力を形成することなくコンプレッサホイールを通した連続流を保証する。 In a typical compressor provided with an overrun air recirculation valve, the compressor housing has an inflow duct that runs from the compressor outlet to the compressor inlet. The inflow duct is controlled by an overrun air recirculation valve to prevent the pumping effect during operation of the exhaust gas turbocharger, the pumping effect being closed, for example, for the braking process of an automobile, This can happen if the exhaust gas turbocharger will still move at high rotational speeds. In this situation, in order to prevent the above effect, the overrun air recirculation valve is opened and the air is directed from the compressor outlet or pressure side to the compressor inlet, thereby creating a high pressure without creating a large pressure. Guarantees continuous flow through.
既知の設計では、流入ダクトはコンプレッサ入口に半径方向に進行し、このことは、流入が排気ガスターボチャージャのシャフトの中心に向かって導かれることを意味する。 In known designs, the inflow duct travels radially to the compressor inlet, which means that the inflow is directed towards the center of the exhaust gas turbocharger shaft.
公知の排気ガスターボチャージャの前記設計を有する本発明に関連して行われた試験は、コンプレッサホイールへの流入方向の結果として流入ダクトの上記の開口部がシャフトに対して半径方向にあるため、流れ騒音が発生し、これにより、前記種類の排気ガスターボチャージャが設けられた車両の動作中に、望ましくない騒音障害をもたらすことがあることを示した。 Tests conducted in connection with the present invention with the above design of known exhaust gas turbochargers have shown that the opening of the inlet duct is radial to the shaft as a result of the inlet direction to the compressor wheel. It has been shown that flow noise is generated, which can lead to undesirable noise disturbances during operation of a vehicle equipped with an exhaust gas turbocharger of the aforementioned kind.
対照的に、本発明の目的は、説明した流れ騒音を回避または著しく低減し、さらには、発生した共振を減衰させることを可能にする請求項１の前段に記載の種類のコンプレッサを提供することである。 In contrast, the object of the present invention is to provide a compressor of the kind set forth in the preceding paragraph of claim 1 which makes it possible to avoid or significantly reduce the described flow noise and furthermore to attenuate the generated resonances. It is.
前記目的は、請求項１の特徴によって達成される。 The object is achieved by the features of claim 1.
前記請求項によれば、流入ダクトは、管状のコンプレッサ入口の管内径に対して少なくとも円周方向にコンプレッサ入口に通じるようにコンプレッサハウジング内に配置される。前記開口部はまた、少なくともほぼ接線方向の開口部と呼んでもよく、この開口部は、接線方向の流入、または圧力側から流入空気に再循環される空気の、円周方向に導かれる流入をもたらし、この流入は、コンプレッサホイールに対して少なくとも実質的に障害の影響を与えず、したがって、少なくとも騒音が実際にもはや認識不可能である程度に、冒頭で説明した流れ騒音を低減する。 According to the claims, the inflow duct is arranged in the compressor housing so as to communicate with the compressor inlet at least in the circumferential direction with respect to the pipe inner diameter of the tubular compressor inlet. The opening may also be referred to as at least a substantially tangential opening, which is a tangential inflow or a circumferentially directed inflow of air recirculated from the pressure side to the inflowing air. This inflow results in at least substantially no disturbing effect on the compressor wheel and thus reduces the flow noise described at the beginning, at least to the extent that the noise is actually no longer recognizable.
ほぼ円周方向に導かれる流入はまた、流入損失を低減するために、流れ方向に向けられた軸方向成分を有してもよい。 The generally circumferentially directed inflow may also have an axial component directed in the flow direction to reduce inflow losses.
このため、コンプレッサ入口には、上記のように流入ダクトが通じる円筒状または切頭円錐状の流入部を設けてもよい。 Therefore, the compressor inlet may be provided with a cylindrical or frustoconical inflow portion through which the inflow duct communicates as described above.
従属請求項は本発明の有利な改良形態に関する。 The dependent claims relate to advantageous refinements of the invention.
特に好ましい実施形態では、再循環される空気の流入がコンプレッサホイールの回転方向に進行するように、流入ダクトがコンプレッサ入口に通じる。しかし、コンプレッサホイールの回転方向と逆方向の流入も原則として可能である。 In a particularly preferred embodiment, the inflow duct leads to the compressor inlet so that the recirculated air inflow proceeds in the direction of rotation of the compressor wheel. However, inflow in the direction opposite to the direction of rotation of the compressor wheel is also possible in principle.
本発明のさらなる詳細、利点および特徴は、図面に基づく例示的な実施形態の以下の説明から明らかになるであろう。 Further details, advantages and features of the invention will become apparent from the following description of exemplary embodiments on the basis of the drawings.
図１は、排気ガス流入口３と排気ガス流出口４とを備えるタービンハウジング２を有する本発明による排気ガスターボチャージャ１を示している。 FIG. 1 shows an exhaust gas turbocharger 1 according to the invention having a turbine housing 2 with an exhaust gas inlet 3 and an exhaust gas outlet 4.
さらに、タービンホイール５がタービンハウジング２内に配置され、このタービンホイールがシャフト６に締結される。 Further, the turbine wheel 5 is disposed in the turbine housing 2, and the turbine wheel is fastened to the shaft 6.
複数のブレードのうちのブレード７のみが示されている当該複数のブレードは、排気ガス流入口３とタービンホイール５との間のタービンハウジング２内に配置される。 The plurality of blades, of which only the blade 7 is shown, are arranged in the turbine housing 2 between the exhaust gas inlet 3 and the turbine wheel 5.
さらに、排気ガスターボチャージャ１はコンプレッサ８を有し、このコンプレッサ８のコンプレッサハウジング１０は、通常、軸受ハウジング９を介してタービンハウジング２に接続される。コンプレッサハウジング１０内において、コンプレッサホイール１１はシャフト６の第２の端部に締結される。図１に示した排気ガスターボチャージャ１に使用してもよい本発明によるコンプレッサ８の２つの実施形態を示している図２〜図４を参照して、本発明によるコンプレッサ８の詳細について以下に説明する。 Further, the exhaust gas turbocharger 1 has a compressor 8, and a compressor housing 10 of the compressor 8 is usually connected to the turbine housing 2 via a bearing housing 9. Within the compressor housing 10, the compressor wheel 11 is fastened to the second end of the shaft 6. Details of the compressor 8 according to the invention will be described below with reference to FIGS. 2 to 4 which show two embodiments of the compressor 8 according to the invention that may be used in the exhaust gas turbocharger 1 shown in FIG. explain.
図２および図３による実施形態は、図２において、コンプレッサホイール１１の関連の回転方向を表す「回転方向ＶＲ」の表示を伴う３つの図示矢印ＶＲで、コンプレッサホイールを明確に示している。コンプレッサホイール１１が図３に示されており、シャフト６に配置される。 The embodiment according to FIGS. 2 and 3 clearly shows the compressor wheel in FIG. 2 with three illustrated arrows VR with an indication of “rotation direction VR” representing the associated rotation direction of the compressor wheel 11. A compressor wheel 11 is shown in FIG.
図２において、オーバーラン空気再循環弁（図では見ることができない）の流入ダクトは参照番号１４で示されており、前記流入ダクト１４は、２つの破線方向に沿って、内径（図４のＤＩ参照）に対してほぼ円周方向にまたは接線方向に開口する。この場合、図３は、流入ダクト開口部１６を明確に示しており、この流入ダクト開口部１６は、コンプレッサ出口１３から再循環される空気の接線方向の流入を許容するように、管状もしくは漏斗状または切頭円錐状の漏斗入口１２に通じる。この場合、図２および図３に明確に示したように、流入は回転方向ＶＲとは逆方向に進行する。 In FIG. 2, the inflow duct of the overrun air recirculation valve (not visible in the figure) is indicated by reference numeral 14, and the inflow duct 14 has an inner diameter (of FIG. 4) along two broken line directions. opening substantially in the circumferential direction or tangentially with respect to D reference I). In this case, FIG. 3 clearly shows the inflow duct opening 16 which is tubular or funneled to allow tangential inflow of air recirculated from the compressor outlet 13. Leading to a conical or frustoconical funnel inlet 12. In this case, as clearly shown in FIGS. 2 and 3, the inflow proceeds in the direction opposite to the rotational direction VR.
図２に追加して示されておりかつ参照符号ＺＫで識別される平行な一点鎖線は、従来技術による流入ダクトの構成を明確に示すのに単に役立つ。破線ＺＫの前記図示は、シャフト６に対して半径方向の流入ダクトの構成を明確に示しており、この構成は、冒頭で説明した問題と関連している。この場合、図２における公知の流入ダクトＺＫの前記追加の図示が、従来技術と本発明との違いを明確に示すのに単に役立つことに再び留意されたい。このような流入ダクトＺＫは、図２および図３による実施形態でも図４による実施形態でも、本発明によるコンプレッサに設けられない。 The parallel dash-dot line additionally shown in FIG. 2 and identified by the reference ZK simply serves to clearly show the configuration of the inflow duct according to the prior art. The illustration of the broken line ZK clearly shows the configuration of the radial inflow duct with respect to the shaft 6 and this configuration is associated with the problem described at the beginning. It should be noted again that in this case the additional illustration of the known inflow duct ZK in FIG. 2 merely serves to clearly show the difference between the prior art and the present invention. Such an inflow duct ZK is not provided in the compressor according to the invention in either the embodiment according to FIGS. 2 and 3 or the embodiment according to FIG.
図４は、本発明によるコンプレッサ８の第２の実施形態を示しており、この第２の実施形態は、図２および図３による実施形態と同様に、自明に、コンプレッサ入口１２（選択された図面では見ることができない）とコンプレッサ出口１３とを有するコンプレッサハウジング１０を有する。図４に破線で同様に示した流入ダクト１５は、直線的に進行する第１のダクト部１５ａと、それに隣接する湾曲したダクト部１５ｂとを有し、このダクト部１５ｂにより、コンプレッサ入口１２の内径ＤＩに対して接線方向またはほぼ円周方向に整列された上記の開口部が得られる。この場合、再循環された空気の流入が、図４の矢印ＶＲで同様に示されているコンプレッサホイール１１の回転方向ＶＲに進行するような開口部が得られる。 FIG. 4 shows a second embodiment of the compressor 8 according to the present invention, which, as is the case with the embodiments according to FIGS. 2 and 3, is obviously the compressor inlet 12 (selected). And a compressor housing 10 having a compressor outlet 13 (not visible in the drawing). The inflow duct 15 similarly indicated by a broken line in FIG. 4 has a first duct portion 15a that linearly advances and a curved duct portion 15b adjacent to the first duct portion 15a. It said openings aligned tangentially or substantially circumferentially is obtained for the internal diameter D I. In this case, an opening is obtained in which the inflow of recirculated air proceeds in the rotational direction VR of the compressor wheel 11 which is also indicated by the arrow VR in FIG.
さらに、本発明の上記の開示に加えて、図１〜図４の、特に図２〜図４の本発明の図面が参照され得る。 Furthermore, in addition to the above disclosure of the present invention, reference may be made to the drawings of the present invention in FIGS.
１ 排気ガスターボチャージャ
２ タービンハウジング
３ 排気ガス流入口
４ 排気ガス流出口
５ タービンホイール
６ シャフト
７ ブレード
８ コンプレッサ
９ 軸受ハウジング
１０ コンプレッサハウジング
１１ コンプレッサホイール
１２ コンプレッサ入口
１３ コンプレッサ出口
１４ オーバーラン空気再循環弁の流入ダクト
１５ オーバーラン空気再循環弁の流入ダクト
１５ａ、ｂ ダクト部
１６ ダクト開口部
ＺＫ 従来技術の流入ダクト
ＶＲ コンプレッサホイール１１の回転方向
ＤＩ コンプレッサ入口１２の内径
1 Exhaust Gas Turbocharger 2 Turbine Housing 3 Exhaust Gas Inlet 4 Exhaust Gas Outlet 5 Turbine Wheel 6 Shaft 7 Blade 8 Compressor 9 Bearing Housing 10 Compressor Housing 11 Compressor Wheel 12 Compressor Inlet 13 Compressor Outlet 14 Compressor Outlet 14 Overrun Air Recirculation Valve inlet ducts 15a of the inlet duct 15 overrun air recirculation valve, the inner diameter of the rotational direction D I compressor inlet 12 of b duct section 16 the duct opening ZK prior art inlet duct VR compressor wheel 11
Claims (4)
−コンプレッサホイール回転方向（ＶＲ）に駆動することができるコンプレッサホイール（１１）を有し、
−流入空気の流れ方向に見たときに、前記コンプレッサホイール（１１）が好ましくは管状のコンプレッサ入口（１２）とコンプレッサ出口（１３）との間に配置されるコンプレッサハウジング（１０）を有し、
−前記コンプレッサハウジング（１０）内で前記コンプレッサ出口（１３）から前記コンプレッサ入口（１２）に進行するオーバーラン空気再循環弁の流入ダクト（１４、１５）を有し、
−前記流入ダクト（１４、１５）が、前記コンプレッサ入口（１２）の内径（ＤＩ）に対してほぼ円周方向に前記コンプレッサ入口（１２）に通じる、
コンプレッサ（８）。 A compressor (8) of an exhaust gas turbocharger (1),
A compressor wheel (11) that can be driven in the direction of rotation of the compressor wheel (VR),
The compressor wheel (11) has a compressor housing (10) arranged between the compressor inlet (12) and the compressor outlet (13), preferably when viewed in the flow direction of the incoming air;
-An inflow duct (14, 15) of an overrun air recirculation valve that travels from the compressor outlet (13) to the compressor inlet (12) in the compressor housing (10);
The inflow duct (14, 15) leads to the compressor inlet (12) in a substantially circumferential direction relative to the inner diameter (D I ) of the compressor inlet (12);
Compressor (8).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010018429 | 2010-04-27 | ||
| DE102010018429.2 | 2010-04-27 | ||
| PCT/US2011/033181 WO2011139561A2 (en) | 2010-04-27 | 2011-04-20 | Compressor of an exhaust-gas turbocharger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2013525685A true JP2013525685A (en) | 2013-06-20 |
Family
ID=44904306
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2013508040A Pending JP2013525685A (en) | 2010-04-27 | 2011-04-20 | Exhaust gas turbocharger compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20130045082A1 (en) |
| JP (1) | JP2013525685A (en) |
| KR (1) | KR20130058689A (en) |
| CN (1) | CN102859143A (en) |
| DE (1) | DE112011101494T5 (en) |
| WO (1) | WO2011139561A2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016011648A (en) * | 2014-06-30 | 2016-01-21 | 本田技研工業株式会社 | Supercharging device of internal combustion engine |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IN2014DN05893A (en) * | 2012-03-06 | 2015-06-05 | Borgwarner Inc | |
| CN103233899B (en) * | 2013-05-20 | 2016-05-04 | 中国南方航空工业(集团)有限公司 | Mechanical pressurizing apparatus and there is the piston engine of this device |
| DE102015215246B4 (en) * | 2015-08-11 | 2022-05-12 | Bayerische Motoren Werke Aktiengesellschaft | Compressor of a turbocharger with a diverter valve and turbocharger and motor vehicle with such a compressor |
| US11378089B2 (en) | 2018-07-06 | 2022-07-05 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Centrifugal compressor and turbocharger |
| DE102020111504A1 (en) | 2020-04-28 | 2021-10-28 | Bayerische Motoren Werke Aktiengesellschaft | Compressor device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56167813A (en) * | 1980-05-28 | 1981-12-23 | Nissan Motor Co Ltd | Surge preventing apparatus for turbocharger |
| JPH11182257A (en) * | 1997-12-19 | 1999-07-06 | Nissan Motor Co Ltd | Centrifugal supercharger |
| JP2010509530A (en) * | 2006-11-09 | 2010-03-25 | ボーグワーナー・インコーポレーテッド | Turbocharger |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH086601B2 (en) * | 1989-05-19 | 1996-01-29 | 三菱重工業株式会社 | Boost pressure control valve device |
| JP2002195046A (en) * | 2000-12-26 | 2002-07-10 | Hitachi Ltd | Exhaust turbine for internal combustion engine and exhaust turbine supercharger |
| WO2007088043A1 (en) * | 2006-02-02 | 2007-08-09 | Borgwarner Inc. | Turbocharger |
| US7475539B2 (en) * | 2006-05-24 | 2009-01-13 | Honeywell International, Inc. | Inclined rib ported shroud compressor housing |
-
2011
- 2011-04-20 KR KR1020127029677A patent/KR20130058689A/en not_active Withdrawn
- 2011-04-20 DE DE112011101494T patent/DE112011101494T5/en not_active Withdrawn
- 2011-04-20 JP JP2013508040A patent/JP2013525685A/en active Pending
- 2011-04-20 US US13/643,097 patent/US20130045082A1/en not_active Abandoned
- 2011-04-20 WO PCT/US2011/033181 patent/WO2011139561A2/en not_active Ceased
- 2011-04-20 CN CN2011800189821A patent/CN102859143A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56167813A (en) * | 1980-05-28 | 1981-12-23 | Nissan Motor Co Ltd | Surge preventing apparatus for turbocharger |
| JPH11182257A (en) * | 1997-12-19 | 1999-07-06 | Nissan Motor Co Ltd | Centrifugal supercharger |
| JP2010509530A (en) * | 2006-11-09 | 2010-03-25 | ボーグワーナー・インコーポレーテッド | Turbocharger |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016011648A (en) * | 2014-06-30 | 2016-01-21 | 本田技研工業株式会社 | Supercharging device of internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011139561A2 (en) | 2011-11-10 |
| CN102859143A (en) | 2013-01-02 |
| WO2011139561A3 (en) | 2012-02-09 |
| KR20130058689A (en) | 2013-06-04 |
| DE112011101494T5 (en) | 2013-02-07 |
| US20130045082A1 (en) | 2013-02-21 |
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