WO2015097890A1 - タービンハウジング - Google Patents
タービンハウジング Download PDFInfo
- Publication number
- WO2015097890A1 WO2015097890A1 PCT/JP2013/085197 JP2013085197W WO2015097890A1 WO 2015097890 A1 WO2015097890 A1 WO 2015097890A1 JP 2013085197 W JP2013085197 W JP 2013085197W WO 2015097890 A1 WO2015097890 A1 WO 2015097890A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- annular
- bearing housing
- turbine housing
- exhaust gas
- annular seal
- Prior art date
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Classifications
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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
- 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
- F01D25/243—Flange connections; Bolting arrangements
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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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
-
- 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
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/162—Bearing supports
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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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
-
- 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
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/026—Scrolls for radial machines or engines
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2230/00—Manufacture
- F05D2230/50—Building or constructing in particular ways
- F05D2230/54—Building or constructing in particular ways by sheet metal manufacturing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/55—Seals
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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
Definitions
- the present invention relates to a turbine housing.
- a turbocharger which supplies pressurized air to an intake manifold by rotating a turbine wheel using energy of exhaust gas led from an engine and rotating a compressor wheel provided coaxially with the turbine wheel. ing.
- weight reduction and heat capacity reduction of the turbocharger have been required, and it has been proposed to use a sheet metal turbine housing instead of the conventional cast turbine housing (see, for example, Patent Document 1). ).
- the contact portion between the turbine housing and the bearing housing of the turbocharger is joined by a bolt or the like. It is desirable to form a seal area on the contact surface of this contact portion to prevent the exhaust gas from leaking from the inside of the turbine housing to the outside.
- the connection portion of the turbine housing and the bearing housing are joined by bolts at a plurality of circumferential positions around the rotation axis of the turbine wheel.
- This invention is made in view of such a situation, and it aims at providing the turbine housing which improved the sealing performance of the contact part of a turbine housing and a bearing housing.
- a turbine housing according to the present invention is a turbine housing connected to a bearing housing rotatably supporting a rotating shaft of a turbine wheel, and is formed in a bottomed cylindrical shape having a peripheral wall portion and a bottom surface portion, and the peripheral wall A scroll portion in which a flange portion protruding in a radial direction orthogonal to the rotation axis is formed at the tip of the portion, and a swirled exhaust gas flow path is formed inside the bottomed cylindrical flow through which exhaust gas flowing from the exhaust gas inlet
- a flat annular lid portion disposed in a state where one end surface is in contact with the flange portion and welded to the flange portion, and a base end portion welded to the inner peripheral side of the other end surface of the annular lid portion
- a plurality of annular seal portions that extend from the proximal end portion toward the distal end portion that is disposed outward in the radial direction and that is formed of an elastically deformable
- the bearing housing is pressed toward the other end surface of the annular lid through the seat surface of the fastener by fastening the fastener in the fastening hole of the connecting part.
- the annular seal is elastically deformed.
- the elastically deformed annular seal portion generates a restoring force in the direction of pressing the tip portion thereof against the outer peripheral surface of the bearing housing, and forms a seal area extending around the rotation axis with the outer peripheral surface of the bearing housing. Do. In this way, it is possible to provide a turbine housing with improved sealing performance at the contact portion between the turbine housing and the bearing housing.
- the scroll portion, the annular lid portion, and the annular seal portion are each formed by processing one sheet metal.
- the turbine housing which improved the sealing performance of the contact part of a turbine housing and a bearing housing can be provided.
- FIG. 6 is a partial enlarged view of the turbocharger shown in FIG. 5, showing a state before the bearing housing is connected to the turbine housing.
- FIG. 6 is a partial enlarged view of the turbocharger shown in FIG. 5 with the bearing housing connected to the turbine housing. It is the elements on larger scale which show the 1st modification of a turbocharger. It is the elements on larger scale which show the 2nd modification of a turbocharger.
- the turbocharger 100 is, for example, a VG (Variable Geometry) turbocharger provided with a variable nozzle mechanism 3.
- the VG turbocharger has a variable nozzle mechanism 3 inside the turbine housing 1.
- the variable nozzle mechanism 3 adjusts the number of rotations of the turbine wheel appropriately by adjusting the flow rate of the introduced exhaust gas by adjusting the nozzle opening degree.
- the turbine housing 1 of the present embodiment is configured by the scroll portion 2, the annular lid portion 6, the annular seal portion 4, and a plurality of screw bushes 16 (connection portions) There is.
- the turbine housing 1 is connected to a bearing housing 30 that rotatably supports a turbine wheel (not shown).
- Reference numeral 7 in FIG. 1 indicates the direction in which the rotation axis of the turbine wheel extends (hereinafter, this direction is referred to as the rotation axis 7).
- the variable nozzle mechanism 3 and a turbine wheel are disposed inside a turbocharger 100 configured by connecting the turbine housing 1 and the bearing housing 3.
- the scroll part 2 is formed in the bottomed cylindrical shape which has the surrounding wall part 20 and the bottom face part 22 as shown in FIG.
- an exhaust gas flow path 2A is formed in a spiral shape along the peripheral wall portion 20 inside the bottomed cylindrical scroll portion 2.
- the exhaust gas outlet 2B penetrates to a position surrounded by the exhaust gas flow path 2A formed in a spiral shape.
- the bottom surface 22 a of the swirling exhaust gas flow channel 2 ⁇ / b> A is formed in a convex shape on the back surface side of the bottom surface portion 22.
- the cross-sectional area of the exhaust gas passage 2A is formed so as to be gradually shallowed from the exhaust gas inlet 24 shown in FIG. 2 and the like toward the exhaust gas outlet 2B.
- the back surface side of the bottom surface portion 22 is formed in a concavo-convex shape, and the bottom surface 22b through which the exhaust gas outlet 2B penetrates and the bottom surface 22a protruding on the back surface side of the bottom surface portion 22 are formed.
- a flange portion 20 a that protrudes in the radial direction orthogonal to the rotation shaft 7 is formed.
- an exhaust gas inlet 24 is formed at the upstream end of the exhaust gas flow path 2A.
- a flat-plate-like engine-side flange 10 is joined to the exhaust gas inlet 24 by welding, for example.
- a fastening hole 10b is formed in the engine side flange portion 10, and is fastened by an exhaust pipe (not shown) and a bolt.
- the high temperature exhaust gas discharged from the engine flows into the exhaust gas inlet 24 of the turbocharger 100 whose exhaust pipe is fastened by the engine side flange portion 10 through the opening 10 a of the engine side flange portion 10.
- the exhaust gas flowing in from the exhaust gas inlet 24 is used as a power to rotate the turbine wheel disposed inside the scroll portion 2 and then flows into the one end 8a of the exhaust unit 8 from the exhaust gas outlet 2B and the other end It is discharged from 8b.
- the annular lid 6 is a flat plate-like member disposed in a state where one end face is in contact with the flange portion 20a, as shown in FIG.
- the circumferential edge of the annular lid 6 in the radial direction and the circumferential edge of the flange 20 a in the radial direction are joined by welding over the entire circumference around the rotation shaft 7. Therefore, the exhaust gas in the exhaust gas flow path 2A does not leak to the outside from the position where the flange portion 20a and one end face of the annular lid 6 abut.
- the annular seal portion 4 is an annular member extending from the proximal end 4a to the distal end 4b, as shown in FIGS. 6 and 7, and is made of an elastically deformable metal member.
- the base end 4a is an inner periphery in the radial direction of the other end surface of the annular lid 6 (a surface different from the contact surface with the flange 20a) with respect to the annular lid 6. Welded to the side.
- the distal end 4b is disposed radially outward of the proximal end 4a.
- the screw bush 16 (connection portion) is welded to the outer peripheral side of the other end surface (a surface different from the contact surface with the flange portion 20a) of the annular lid 6 as shown in FIG. 5 to FIG. As shown in FIGS. 2 to 4, the screw bushes 16 are respectively welded to a plurality of locations in the circumferential direction of the annular lid 6. As shown in FIG. 5 and FIG. 7, a fastener composed of a bolt 40 and a washer 41 is inserted into and coupled to the screw bush 16 along the rotation shaft 7.
- reference numeral 20 b indicates a tongue that constitutes a winding end portion of the exhaust gas flow path 2 ⁇ / b> A formed in a spiral shape.
- the plurality of screw bushes 16 are arranged substantially equally in the circumferential direction, but the screw bushes 16 may be arranged at a closer distance in the vicinity of the tongue portion 20b. In this way, it is possible to more reliably prevent the exhaust gas from leaking in the vicinity of the tongue portion 20b where the possibility of deformation due to thermal effects is high.
- a male screw portion is formed on the outer peripheral surface of the bolt 40, and a female screw portion is formed on the inner peripheral surface of the fastening hole 16b of the screw bush 16.
- the male screw portion of the bolt 40 is fastened to the female screw portion of the screw bush 16 by rotating the bolt 40.
- the flange portion 30 a of the bearing housing 30 is pressed against the annular lid 6 through the bearing surface of the washer 41 of the fastener 42 as the tip 4 b of the annular seal 4.
- the outer circumferential surface 30 c of the bearing housing 30 is contacted.
- the annular seal part 4 is elastically deformed from the state shown in FIG. 6 to the state shown in FIG.
- the annular seal portion 4 When the annular seal portion 4 is elastically deformed as shown in FIG. 7, the annular seal portion 4 generates a restoring force in the direction of pressing the tip portion 4 b against the outer peripheral surface 30 c of the bearing housing 30. As a result, a seal area extending around the entire rotation axis 7 is formed between the tip 4 b of the annular seal portion 4 and the outer peripheral surface 30 c of the bearing housing 30.
- the annular seal portion 4 is restored so that the distal end portion 4 b is pressed against the outer peripheral surface 30 c of the bearing housing 30 because the distal end portion 4 b is disposed radially outside the proximal end portion 4 a.
- the force has a component in the direction of the axis of rotation towards the bearing housing 30 along the axis of rotation 7 and a component in the radial direction towards the center of the axis of rotation 7 along the radial direction perpendicular to the axis of rotation 7 become. Since the restoring force has a radial component, the bearing housing 30 is given a restoring force that moves it from the seal region extending all around its circumferential direction toward the center of the rotating shaft 7. Thus, the bearing housing 30 is adjusted so as not to be misaligned.
- the scroll portion 2, the annular lid portion 6 and the annular seal portion 4 constituting the turbine housing 1 are each formed by processing a single thin plate. That is, it is formed by plastically deforming a flat sheet metal into a predetermined shape by a method such as bending or pressing, and partially cutting out an unnecessary portion by punching or the like.
- heat-resistant steels such as austenitic stainless steel, are used suitably, for example.
- the bearing housing 30 has an annular shape via the bearing surface of the washer 41 by fastening the bolt 40 to the fastening hole 16 b of the screw bush 16 (connection portion). It is pressed toward the other end face of the lid 6.
- the annular seal 4 is elastically deformed.
- the elastically deformed annular seal portion 4 generates a restoring force in the direction to press the tip portion 4 b against the outer peripheral surface 30 c of the bearing housing 30, and the entire circumference around the rotational shaft 7 with the outer peripheral surface 30 c of the bearing housing 30.
- Form an extending seal area In this way, it is possible to provide the turbine housing 1 in which the sealing performance of the contact portion between the turbine housing 1 and the bearing housing 30 is enhanced.
- the scroll portion 2, the annular lid portion 6 and the annular seal portion 4 are formed by processing one sheet metal. By doing this, it is possible to provide the turbine housing 1 which is reduced in weight and reduced in heat capacity.
- the shape of the annular seal portion is the shape shown in FIGS. 6 and 7, it may be another aspect.
- the shape of the annular seal 4 'of the first modification shown in FIG. 8 may be used.
- the length L2 from the base end 4'a to the change point 4'c where the inclination angle changes along the rotation axis 7 is from the change point 4'c to the tip end Longer than length L1 up to 4'b.
- the angle ⁇ 1 formed by the outer circumferential surface 30'c of the flange portion 30'a of the bearing housing 30 'and the annular seal portion 4' is large.
- the shape of the annular seal portion may be, for example, the shape of the annular seal portion 4 ′ ′ of the second modification shown in FIG.
- the length L4 from the base end 4′′a to the change point 4′′c where the inclination angle changes along the rotation axis 7 is a change point 4 ′ ′
- the length L3 from c to the tip 4 ′ ′ b is substantially the same.
- the angle ⁇ 2 formed by the outer peripheral surface 30 "c of the flange portion 30" a of the bearing housing 30 "and the annular seal portion 4" is smaller than ⁇ 1.
- the shape of the annular seal portion may be appropriately selected according to the internal pressure and the amount of thermal deformation generated in the turbine housing, other than those exemplified in the first and second modifications. It shall be possible.
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Abstract
Description
特許文献1では、タービンハウジングの連結部とベアリングハウジングとが、タービンホイールの回転軸回りの周方向の複数箇所でボルトにより接合されている。
本発明に係るタービンハウジングは、タービンホイールの回転軸を回転可能に支持するベアリングハウジングに連結されるタービンハウジングであって、周壁部と底面部とを有する有底筒状に形成されるとともに該周壁部の先端に前記回転軸に直交する径方向に突出するフランジ部が形成され、該有底筒状の内部に排ガス流入口から流入した排ガスが流れる渦状の排ガス流路が形成されたスクロール部と、前記フランジ部に一端面が当接した状態で配置され、該フランジ部と溶接された平板状の環状蓋部と、前記環状蓋部の他端面の内周側に溶接される基端部から該基端部より前記径方向の外側に配置される先端部に向けて延在し、弾性変形可能な部材で構成される環状シール部と、前記環状蓋部の前記他端面の外周側の複数箇所にそれぞれ溶接され、前記回転軸方向に沿って挿入される締結具が締結される締結穴を有する複数の連結部とを備え、前記環状シール部が、前記締結具の座面を介して前記ベアリングハウジングが前記環状蓋部に向けて押し付けられることにより、該ベアリングハウジングの外周面に前記先端部が接触して弾性変形し、前記回転軸回りの全周に延在するシール領域を形成する。
このようにすることで、タービンハウジングとベアリングハウジングとの接触部のシール性能を高めたタービンハウジングを提供することができる。
このようにすることで、軽量化および低熱容量化がなされたタービンハウジングを提供することができる。
本実施形態のターボチャージャ100は、例えば、可変ノズル機構3を備えたVG(Variable Geometry)ターボチャージャである。VGターボチャージャは、タービンハウジング1の内部に可変ノズル機構3を備えている。可変ノズル機構3は、ノズル開度の調整によって導入する排ガスの流量を調整することにより、タービンホイールの回転数を適切に調整するものである。
タービンハウジング1とベアリングハウジング3とが連結されて構成されるターボチャージャ100の内部には、可変ノズル機構3とタービンホイールが配置されている。
また、図5に示すように、スクロール部2の周壁部20の先端には、回転軸7に直交する径方向に突出するフランジ部20aが形成されている。
このようにすることで、タービンハウジング1とベアリングハウジング30との接触部のシール性能を高めたタービンハウジング1を提供することができる。
このようにすることで、軽量化および低熱容量化がなされたタービンハウジング1を提供することができる。
以上の説明においては、環状シール部の形状を図6および図7に示す形状としたが、他の態様であってもよい。例えば、図8に示す第1変形例の環状シール部4′の形状としてもよい。
第1変形例の環状シール部4′は、回転軸7に沿って基端部4′aから傾斜角が変化する変化点4′cまでの長さL2が、変化点4′cから先端部4′bまでの長さL1よりも長い。また、ベアリングハウジング30′のフランジ部30′aの外周面30′cと環状シール部4′とがなす角θ1が大きくなっている。
図8に示す環状シール部4′の形状とすることにより、先端部4′bにおける弾性変形の変位量を増大させ、それに伴って復元力を増大させることができる。
第1変形例の環状シール部4′′は、回転軸7に沿って基端部4′′aから傾斜角が変化する変化点4′′cまでの長さL4が、変化点4′′cから先端部4′′bまでの長さL3とほぼ同じである。また、ベアリングハウジング30′′のフランジ部30′′aの外周面30′′cと環状シール部4′′とがなす角θ2がθ1よりも小さくなっている。
図9に示す環状シール部4′′の形状とすることにより、締結による反力が比較的低下するものの、熱変形による追随性が向上する。そのため、タービンハウジングの熱変形量が大きい場合であってもシール性能が向上する。
2 スクロール部
4 環状シール部
4a 基端部
4b 先端部
6 環状蓋部
7 回転軸
16 ネジブッシュ(連結部)
16a 外側端面
16b 締結穴
20 周壁部
20a フランジ部
22 底面部
22a 底面
24 排ガス流入口
30 ベアリングハウジング
30a フランジ部
30b,30c 外周面
40 ボルト
40a 頭部
41 座金
42 締結具
100 ターボチャージャ
Claims (2)
- タービンホイールの回転軸を回転可能に支持するベアリングハウジングに連結されるタービンハウジングであって、
周壁部と底面部とを有する有底筒状に形成されるとともに該周壁部の先端に前記回転軸に直交する径方向に突出するフランジ部が形成され、該有底筒状の内部に排ガス流入口から流入した排ガスが流れる渦状の排ガス流路が形成されたスクロール部と、
前記フランジ部に一端面が当接した状態で配置され、該フランジ部と溶接された平板状の環状蓋部と、
前記環状蓋部の他端面の内周側に溶接される基端部から該基端部より前記径方向の外側に配置される先端部に向けて延在し、弾性変形可能な部材で構成される環状シール部と、
前記環状蓋部の前記他端面の外周側の複数箇所にそれぞれ溶接され、前記回転軸方向に沿って挿入される締結具が締結される締結穴を有する複数の連結部とを備え、
前記環状シール部が、前記締結具の座面を介して前記ベアリングハウジングが前記環状蓋部に向けて押し付けられることにより、該ベアリングハウジングの外周面に前記先端部が接触して弾性変形し、前記回転軸回りの全周にシール領域を形成するタービンハウジング。 - 前記スクロール部と前記環状蓋部と前記環状シール部とが、それぞれ1枚の板金を加工することにより形成されている請求項1に記載のタービンハウジング。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13899987.5A EP3088698B1 (en) | 2013-12-27 | 2013-12-27 | Turbine housing |
JP2015554468A JP6026020B2 (ja) | 2013-12-27 | 2013-12-27 | タービンハウジング |
CN201380080206.3A CN105637194B (zh) | 2013-12-27 | 2013-12-27 | 涡轮壳体 |
PCT/JP2013/085197 WO2015097890A1 (ja) | 2013-12-27 | 2013-12-27 | タービンハウジング |
US15/031,436 US10077679B2 (en) | 2013-12-27 | 2013-12-27 | Turbine housing |
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Application Number | Priority Date | Filing Date | Title |
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PCT/JP2013/085197 WO2015097890A1 (ja) | 2013-12-27 | 2013-12-27 | タービンハウジング |
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WO2015097890A1 true WO2015097890A1 (ja) | 2015-07-02 |
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US (1) | US10077679B2 (ja) |
EP (1) | EP3088698B1 (ja) |
JP (1) | JP6026020B2 (ja) |
CN (1) | CN105637194B (ja) |
WO (1) | WO2015097890A1 (ja) |
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---|---|---|---|---|
US11732729B2 (en) * | 2021-01-26 | 2023-08-22 | Garrett Transportation I Inc | Sheet metal turbine housing |
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2013
- 2013-12-27 WO PCT/JP2013/085197 patent/WO2015097890A1/ja active Application Filing
- 2013-12-27 EP EP13899987.5A patent/EP3088698B1/en not_active Not-in-force
- 2013-12-27 JP JP2015554468A patent/JP6026020B2/ja active Active
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JP2009047027A (ja) * | 2007-08-16 | 2009-03-05 | Ihi Corp | ターボチャージャ |
JP2010138885A (ja) * | 2008-12-15 | 2010-06-24 | Toyota Motor Corp | ターボチャージャ |
WO2013141379A1 (ja) * | 2012-03-23 | 2013-09-26 | 三菱重工業株式会社 | タービンハウジングアセンブリおよびタービンハウジングアセンブリの製造方法 |
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WO2013187448A1 (ja) * | 2012-06-15 | 2013-12-19 | 株式会社Ihi | シール構造及び可変容量型過給機 |
Also Published As
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US20160258325A1 (en) | 2016-09-08 |
CN105637194A (zh) | 2016-06-01 |
CN105637194B (zh) | 2018-07-24 |
EP3088698A4 (en) | 2018-01-03 |
EP3088698A1 (en) | 2016-11-02 |
US10077679B2 (en) | 2018-09-18 |
JPWO2015097890A1 (ja) | 2017-03-23 |
JP6026020B2 (ja) | 2016-11-16 |
EP3088698B1 (en) | 2018-12-19 |
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