WO2012176866A1 - Système de surcompression à multiples étages - Google Patents

Système de surcompression à multiples étages Download PDF

Info

Publication number
WO2012176866A1
WO2012176866A1 PCT/JP2012/065958 JP2012065958W WO2012176866A1 WO 2012176866 A1 WO2012176866 A1 WO 2012176866A1 JP 2012065958 W JP2012065958 W JP 2012065958W WO 2012176866 A1 WO2012176866 A1 WO 2012176866A1
Authority
WO
WIPO (PCT)
Prior art keywords
supercharger
valve body
exhaust gas
stopper
supercharging system
Prior art date
Application number
PCT/JP2012/065958
Other languages
English (en)
Japanese (ja)
Inventor
大博 本間
謙治 文野
Original Assignee
株式会社Ihi
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 株式会社Ihi filed Critical 株式会社Ihi
Publication of WO2012176866A1 publication Critical patent/WO2012176866A1/fr

Links

Images

Classifications

    • 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
    • F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
    • 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
    • F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
    • 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
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • 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
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • 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
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • F02B37/186—Arrangements of actuators or linkage for bypass valves
    • 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 multistage supercharging system.
  • This application claims priority based on Japanese Patent Application No. 2011-138310 filed in Japan on June 22, 2011, the contents of which are incorporated herein by reference.
  • a two-stage supercharging system (multi-stage supercharging system) having two (or a plurality) superchargers has been proposed.
  • Such a two-stage supercharging system includes two superchargers having different capacities, and changes the supply state of exhaust gas to the two superchargers according to the flow rate of exhaust gas supplied from the internal combustion engine. To generate compressed air efficiently.
  • the two-stage turbocharging system includes, for example, a low-pressure supercharger (first supercharger) to which exhaust gas discharged from an internal combustion engine is supplied, and an upstream side of the low-pressure supercharger. And a bypass passage for supplying exhaust gas discharged from the internal combustion engine to the low pressure turbocharger by bypassing the turbine impeller of the high pressure turbocharger And an exhaust bypass valve device that opens and closes.
  • a low-pressure supercharger first supercharger
  • a bypass passage for supplying exhaust gas discharged from the internal combustion engine to the low pressure turbocharger by bypassing the turbine impeller of the high pressure turbocharger
  • an exhaust bypass valve device that opens and closes.
  • the exhaust bypass valve device disclosed in Patent Document 2 can be applied.
  • the exhaust gas When the bypass passage is closed by the exhaust bypass valve device, the exhaust gas is supplied to the high pressure supercharger, and when the bypass passage is opened by the exhaust bypass valve device, the exhaust gas is supplied to the low pressure stage supercharger. It is comprised so that it may be supplied to.
  • the exhaust bypass valve device includes a valve body that directly opens and closes the bypass flow path.
  • the valve body is connected to the actuator via a mediating member such as a link plate or an attachment portion, and is configured to open and close when the power of the actuator is transmitted.
  • the valve body when assembling a two-stage supercharging system, for example, the valve body is connected to the actuator by welding and joining the mediating members.
  • the relationship between the maximum displacement of the actuator and the maximum opening of the valve body after the valve body is installed due to individual differences in the actuator and mounting errors of the valve body and the mediating member. If the relationship between the maximum displacement of the actuator and the maximum opening of the valve body varies, the maximum opening of the valve body varies. For this reason, the flow rate of the exhaust gas flowing through the bypass flow path, that is, the flow rate of the exhaust gas supplied to the low-pressure supercharger changes for each individual two-stage turbocharging system, resulting in performance variations in the internal combustion engine.
  • the present invention has been made in view of the above-described problems, and an object of the present invention is to stabilize the flow rate of exhaust gas flowing through a bypass passage in a multistage supercharging system.
  • the present invention adopts the following configuration as means for solving the above-described problems.
  • a first supercharger to which exhaust gas discharged from an internal combustion engine is supplied, and a second supercharger disposed on the upstream side of the exhaust gas flow from the first supercharger.
  • a valve body that adjusts an opening degree of a bypass passage that bypasses the turbine impeller of the second supercharger and supplies the exhaust gas discharged from the internal combustion engine to the first supercharger.
  • the supercharging system is configured to include a stopper that defines the maximum opening of the valve body.
  • the second invention employs a configuration in which, in the first invention, the stopper is attached to the turbine housing and the attachment position with respect to the turbine housing is adjustable.
  • a third invention is the screw according to the second invention, further comprising a link plate for transmitting the power of the actuator to the valve body, wherein the stopper is screwed to the turbine housing and contacts the link plate.
  • the structure of being a member is adopted.
  • the protrusion in the first aspect of the present invention, includes a mounting portion that is rotated by the actuator and to which the valve body is mounted, and the stopper is provided on the mounting portion and contacts the turbine housing.
  • the configuration of being is adopted.
  • regulating the maximum opening degree of a valve body is provided separately. Since this stopper is used only for defining the maximum opening of the valve body, the maximum opening of the valve body can be defined without affecting other functions. Therefore, according to the present invention, it is possible to install the stopper so that individual differences of actuators and valve body mounting errors are cancelled. In addition, it is possible to prevent variation in the relationship between the maximum displacement of the actuator and the maximum opening of the valve body. Therefore, the maximum opening of the valve body when the actuator is displaced to the maximum is always the same, and the flow rate of the exhaust gas flowing through the bypass passage can be stabilized.
  • FIG. 1 It is a schematic diagram including the two-stage supercharging system in 1st Embodiment of this invention. It is principal part sectional drawing containing the two-stage supercharging system in 1st Embodiment of this invention. It is a disassembled perspective view containing the valve assembly and attachment plate with which the two-stage supercharging system in 1st Embodiment of this invention is provided. It is a side view containing the valve assembly and attachment plate with which the two-stage supercharging system in 1st Embodiment of this invention is provided. It is a perspective view containing the valve assembly and attachment plate with which the two-stage supercharging system in 2nd Embodiment of this invention is provided. It is a side view containing the valve assembly and attachment plate with which the two-stage supercharging system in 2nd Embodiment of this invention is provided.
  • Drawing 1A is a mimetic diagram showing a schematic structure of engine system 100 provided with two-stage supercharging system 1 of this embodiment.
  • the engine system 100 is mounted on a vehicle or the like, and includes a two-stage turbocharging system 1, an engine 101 (internal combustion engine), an intercooler 102, an EGR (Exhaust Gas Recirculation) valve 103, an EGR cooler 104, and an ECU (Engine). Control Unit) 105.
  • the two-stage supercharging system 1 collects energy contained in exhaust gas discharged from the engine 101 as rotational power, and generates compressed air to be supplied to the engine 101 by the rotational power.
  • the two-stage supercharging system 1 will be described in detail later with reference to the drawings.
  • the engine 101 functions as a power source for the vehicle on which it is mounted, and generates power by burning a mixture of compressed air and fuel supplied from the two-stage supercharging system 1, and exhaust generated by the combustion of the mixture Gas is supplied to the two-stage supercharging system 1.
  • the intercooler 102 cools the compressed air supplied from the two-stage supercharging system 1 to the engine 101 and is disposed between the two-stage supercharging system 1 and the intake port of the engine 101.
  • the EGR valve 103 opens and closes a return flow path for returning a part of the exhaust gas discharged from the engine 101 to the intake side of the engine 101, and its opening degree is adjusted by the ECU 105.
  • the EGR cooler 104 cools the exhaust gas that is returned to the intake side of the engine 101 via the return flow path, and is disposed on the upstream side of the EGR valve 103.
  • the ECU 105 controls the entire engine system 100.
  • the ECU 105 controls the above-described EGR valve 103 and an exhaust bypass valve device 5 described later in accordance with the rotational speed of the engine 101 (that is, the exhaust gas flow rate).
  • the engine system 100 having the above-described configuration, when the exhaust gas in which the air-fuel mixture is combusted in the engine 101 is exhausted, a part of the exhaust gas is returned to the intake side of the engine 101 via the EGR cooler 104, Most of the exhaust gas is supplied to the two-stage supercharging system 1. Then, compressed air is generated in the two-stage supercharging system 1, and the compressed air is cooled by the intercooler 102 and then supplied to the engine 101.
  • a two-stage supercharging system 1 includes a low-pressure supercharger 2 (first supercharger), a high-pressure supercharger 3 (second supercharger), a check valve 4, The exhaust bypass valve device 5 and the waste gate valve 6 are provided.
  • the low-pressure stage supercharger 2 is arranged downstream of the high-pressure stage supercharger 3 in the exhaust gas flow direction, and is configured to be larger than the high-pressure stage supercharger 3.
  • the low-pressure supercharger 2 includes a low-pressure compressor 2a and a low-pressure turbine 2b.
  • the low-pressure compressor 2a includes a compressor impeller and a compressor housing that surrounds the compressor impeller and has an air flow path formed therein.
  • the low-pressure turbine 2b includes a turbine impeller and a turbine housing that surrounds the turbine impeller and has an exhaust gas passage formed therein.
  • the compressor impeller and the turbine impeller are connected by a shaft, and the turbine impeller is rotationally driven by the exhaust gas, whereby the compressor impeller is rotationally driven to generate compressed air.
  • the high-pressure supercharger 3 is arranged upstream of the low-pressure supercharger 2 in the exhaust gas flow direction.
  • the high-pressure supercharger 3 includes a high-pressure compressor 3a and a high-pressure turbine 3b.
  • the high-pressure compressor 3a includes a compressor impeller and a compressor housing that surrounds the compressor impeller and has an air passage formed therein.
  • the high-pressure turbine 3b includes a turbine impeller and a turbine housing that surrounds the turbine impeller and has an exhaust gas passage formed therein.
  • the compressor impeller and the turbine impeller are connected by a shaft, and the turbine impeller is rotationally driven by the exhaust gas, whereby the compressor impeller is rotationally driven to generate compressed air.
  • the turbine housing 2c of the low-pressure stage turbine 2b and the turbine housing 3c of the high-pressure stage turbine 3b are joined to each other by abutting flanges.
  • an exhaust passage 3d for discharging exhaust gas that has passed through the turbine impeller of the high-pressure turbine 3b, and for supplying the low-pressure turbine 2b without passing through the turbine impeller.
  • a bypass channel 3e is provided inside the turbine housing 3c of the high-pressure turbine 3b.
  • a supply flow path 2e for supplying exhaust gas to the turbine impeller 2d of the low-pressure turbine 2b is provided inside the turbine housing 2c of the low-pressure turbine 2b.
  • the turbine housing 2c of the low-pressure turbine 2b and the turbine housing 3c of the high-pressure turbine 3b are joined to connect the exhaust passage 3d, the bypass passage 3e, and the supply passage 2e.
  • the check valve 4 generates high-pressure compressed air discharged from the low-pressure stage compressor 2 a of the low-pressure supercharger 2 when the high-pressure stage compressor 3 a of the high-pressure supercharger 3 is not driven. It is provided in a bypass flow path that supplies the intake side of the engine 101 without going through the stage compressor 3a. As shown in FIG. 1A, the check valve 4 allows the flow of compressed air from the low-pressure stage compressor 2a side to the engine 101 side and the backflow of compressed air from the engine 101 side to the low-pressure stage compressor 2a side. Is configured to prevent.
  • the exhaust bypass valve device 5 opens and closes a bypass flow path 3 e for supplying exhaust gas discharged from the engine 101 to the low pressure turbocharger 2 by bypassing the turbine impeller of the high pressure turbocharger 3.
  • the exhaust bypass valve device 5 includes a valve assembly 51, a mounting plate 52 (mounting portion), a link plate assembly 53, and an actuator 54.
  • FIG. 2A is an exploded perspective view including the valve assembly 51, the mounting plate 52, and the link plate assembly 53.
  • FIG. 2B is an enlarged view of a main part of the turbine housing 3 c including the valve assembly 51, the mounting plate 52, and the link plate assembly 53.
  • the valve assembly 51 has a configuration in which a valve body 51a that opens and closes an opening of the bypass passage 3e and a washer 51b that fixes the valve body 51a to the mounting plate 52 are connected via a shaft portion 51c. have.
  • the valve assembly 51 is rotatable so as to open and close the opening of the bypass passage 3e in the boundary region between the turbine housing 2c of the low-pressure turbine 2b and the turbine housing 3c of the high-pressure turbine 3b. ing.
  • a through hole is provided at the center of the washer 51b, and the shaft 51c is inserted into the through hole of the washer 51b from above the valve body 51a, so that the tip of the shaft 51c protrudes from the washer 51b.
  • the shaft 51c and the washer 51b are fixed by welding the tip of the shaft 51c and the washer 51b.
  • the mounting plate 52 has a through hole through which the shaft portion 51c is inserted.
  • the shaft portion 51c is inserted through the through hole, and is sandwiched between the valve body 51a and the washer 51b.
  • the mounting plate 52 includes a fitting hole 52a into which a stem 53b of a link plate assembly 53 described later is inserted.
  • the link plate assembly 53 includes a link plate 53a whose one end is rotatably connected to the actuator rod 54a, and a stem 53b fixed to the other end of the link plate 53a.
  • the stem 53 b penetrates the turbine housing 3 c and is welded to the mounting plate 52 of the valve assembly 51 at the tip.
  • the two-stage turbocharging system 1 of the present embodiment includes a stopper 10 attached to the turbine housing 3c.
  • the stopper 10 prescribes
  • the stopper 10 is constituted by a screw member that is fixed by being screwed to the turbine housing 3c. The stopper 10 abuts against the link plate 53a and rotates the link plate 53a. By restricting the movement, the maximum rotation angle of the link plate 53a (that is, the maximum opening of the valve body 51a) is defined.
  • the stopper 10 is screwed into the turbine housing 3c via a nut 11, and can be moved in the left-right direction in FIG. 2B by rotating the nut 11. That is, in this embodiment, the stopper 10 is attached to the turbine housing 3c and the attachment position relative to the turbine housing 3c is adjustable. By changing the attachment position of the stopper 10 with respect to the turbine housing 3c, the contact position between the stopper 10 and the link plate 53a changes, and the maximum opening degree of the valve body 51a can be adjusted.
  • a negative pressure operating actuator when assembling the two-stage turbocharging system 1 of the present embodiment, first, a set pressure for fully closing the valve body 51a is applied to the actuator 54. After that, the valve assembly 51, the mounting plate 52, and the link plate assembly 53 are connected by welding or the like. Thereafter, the pressure applied to the actuator 54 is gradually released, and the mounting position of the stopper 10 is adjusted so that the rotation angle of the valve body 51a becomes the maximum angle required in advance.
  • the wastegate valve 6 uses the exhaust gas discharged from the high-pressure supercharger 3 or a part of the exhaust gas discharged via the bypass flow passage 3 e to convert the turbine impeller of the low-pressure supercharger 2. Bypassing without passing through 2d, the opening degree is adjusted by the supercharging pressure of the ECU 105 or the low-pressure compressor 2a.
  • the stopper 10 for defining the maximum opening degree of the valve body 51a is provided as a separate body. Since the stopper 10 is used only for defining the maximum opening of the valve body 51a, the maximum opening of the valve body 51a can be defined without affecting other functions. Therefore, according to the two-stage supercharging system 1 of the present embodiment, the stopper 10 can be installed so that individual differences of the actuators 54 and mounting errors of the valve body 51a can be canceled, and the maximum displacement amount ( It is possible to prevent variation in the relationship between the stroke amount of the actuator rod 54a) and the maximum opening of the valve body 51a. Therefore, the maximum opening degree of the valve body 51a when the actuator 54 is displaced to the maximum is always the same, and the flow rate of the exhaust gas flowing through the bypass passage 3e can be stabilized.
  • the attachment position with respect to the turbine housing 3c of the stopper 10 can be adjusted. For this reason, by finely adjusting the position of the stopper 10 at the time of assembly, it is possible to more reliably prevent variations in the relationship between the maximum displacement amount of the actuator 54 and the maximum opening degree of the valve body 51a.
  • the structure which the stopper 10 consists of a bolt member was employ
  • the stopper 10 since the stopper 10 is attached to the outside of the turbine housing 3c, the stopper 10 is prevented from touching the exhaust gas, and corrosion of the stopper 10 is prevented. be able to.
  • FIG. 3A is a perspective view of the valve assembly 51 and the mounting plate 52 provided in the two-stage supercharging system of the present embodiment.
  • FIG. 3B is a side view including the valve assembly 51, the mounting plate 52, and a part of the turbine housing 3c included in the two-stage turbocharging system of the present embodiment.
  • the two-stage turbocharging system of the present embodiment includes a stopper 20 provided on the mounting plate 52 in place of the stopper 10 of the first embodiment.
  • the stopper 20 is formed of a protruding portion that comes into contact with the built-up portion 3c1 provided in the turbine housing 3c, and regulates the maximum opening of the valve body 51a by coming into contact with the built-up portion 3c1.
  • the stopper 20 for defining the maximum opening degree of the valve body 51a is provided as a separate body. Since the stopper 20 is used only for defining the maximum opening of the valve body 51a, the maximum opening of the valve body 51a can be defined without affecting other functions. According to the two-stage supercharging system of the present embodiment, the stopper 20 can be installed so that individual differences of the actuators 54 and mounting errors of the valve body 51a are cancelled. In addition, it is possible to prevent variation in the relationship between the maximum displacement amount of the actuator 54 (stroke amount of the actuator rod 54a) and the maximum opening degree of the valve body 51a. Therefore, the maximum opening degree of the valve body 51a when the actuator 54 is displaced to the maximum is always the same, and the flow rate of the exhaust gas flowing through the bypass passage 3e can be stabilized.
  • the configuration including two superchargers has been described.
  • the present invention is not limited to this, and a configuration including a plurality of superchargers can also be employed.
  • the maximum opening of the valve body can be defined without affecting other functions, so that individual differences of actuators and valve body mounting errors are cancelled.
  • a stopper can be installed. Further, it is possible to prevent variation in the relationship between the maximum displacement amount of the actuator and the maximum opening degree of the valve body, and it is possible to stabilize the flow rate of the exhaust gas flowing through the bypass passage.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)

Abstract

La présente invention porte sur un système de surcompression à multiples étages qui comporte : un premier surcompresseur (2) auquel un gaz d'échappement déchargé à partir d'un moteur à combustion interne (101) est fourni ; un second surcompresseur (3) disposé sur le côté amont du premier surcompresseur (2) par rapport à l'écoulement de gaz d'échappement ; un corps de valve (51a) qui ajuste le degré d'ouverture d'un conduit de dérivation (3e) qui fourni le gaz d'échappement déchargé à partir du moteur à combustion interne (101) au premier surcompresseur (2) dérivant la roue de turbine (2d) du second surcompresseur (3) ; et une butée (10) qui délimite le degré maximal d'ouverture du corps de valve (51a).
PCT/JP2012/065958 2011-06-22 2012-06-22 Système de surcompression à multiples étages WO2012176866A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011138310A JP2013007265A (ja) 2011-06-22 2011-06-22 多段過給システム
JP2011-138310 2011-06-22

Publications (1)

Publication Number Publication Date
WO2012176866A1 true WO2012176866A1 (fr) 2012-12-27

Family

ID=47422694

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/065958 WO2012176866A1 (fr) 2011-06-22 2012-06-22 Système de surcompression à multiples étages

Country Status (2)

Country Link
JP (1) JP2013007265A (fr)
WO (1) WO2012176866A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107035510A (zh) * 2016-01-29 2017-08-11 大众汽车有限公司 用于内燃机的废气涡轮增压器
CN113339127A (zh) * 2021-05-10 2021-09-03 重庆长安汽车股份有限公司 一种用于增压器的废气旁通阀总成及车辆

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6954471B2 (ja) 2018-07-10 2021-10-27 株式会社Ihi 改竄防止構造

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62193136U (fr) * 1986-05-29 1987-12-08
JPH0725248U (ja) * 1993-10-01 1995-05-12 富士重工業株式会社 過給機付エンジン
WO2007058017A1 (fr) * 2005-11-18 2007-05-24 Isuzu Motors Limited Systeme de suralimentation a deux etages pour moteur a combustion interne
JP2011021504A (ja) * 2009-07-14 2011-02-03 Isuzu Motors Ltd 多段過給装置
JP2012140889A (ja) * 2010-12-28 2012-07-26 Isuzu Motors Ltd 切替式二段過給機ターボシステム

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2605721Y2 (ja) * 1993-09-29 2000-08-07 富士重工業株式会社 過給機付エンジン
JPH1122833A (ja) * 1997-07-03 1999-01-26 Kubota Corp バタフライ弁

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62193136U (fr) * 1986-05-29 1987-12-08
JPH0725248U (ja) * 1993-10-01 1995-05-12 富士重工業株式会社 過給機付エンジン
WO2007058017A1 (fr) * 2005-11-18 2007-05-24 Isuzu Motors Limited Systeme de suralimentation a deux etages pour moteur a combustion interne
JP2011021504A (ja) * 2009-07-14 2011-02-03 Isuzu Motors Ltd 多段過給装置
JP2012140889A (ja) * 2010-12-28 2012-07-26 Isuzu Motors Ltd 切替式二段過給機ターボシステム

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107035510A (zh) * 2016-01-29 2017-08-11 大众汽车有限公司 用于内燃机的废气涡轮增压器
CN113339127A (zh) * 2021-05-10 2021-09-03 重庆长安汽车股份有限公司 一种用于增压器的废气旁通阀总成及车辆

Also Published As

Publication number Publication date
JP2013007265A (ja) 2013-01-10

Similar Documents

Publication Publication Date Title
US8695338B2 (en) Exhaust gas control apparatus for engine
KR101794365B1 (ko) 내연 엔진용 신선 가스 공급 장치 및 이런 신선 가스 공급 장치의 작동 방법
US8074628B2 (en) Air intake device for a heat engine with a cooled main circulation system and a bypass system equipped with a heating mechanism
US20130025576A1 (en) Multifunction valve
JP2010014271A (ja) 弁調整組立体
US20130309106A1 (en) Turbocharger
JP5919663B2 (ja) 多段過給システム
WO2012176866A1 (fr) Système de surcompression à multiples étages
US8069664B2 (en) Integrated inlet and bypass throttle for positive-displacement supercharged engines
JP5728943B2 (ja) ターボシステム及び切替式二段過給機ターボシステム
WO2007089737A1 (fr) Combinaison de compresseur a geometrie variable, robinet d'etranglement, et robinet de recirculation
JP5845650B2 (ja) ウエストゲートバルブ
US9708970B2 (en) Housing for turbocharger
JP2015059506A (ja) バルブ装置
KR20150132219A (ko) 소형 회전 웨이스트게이트 밸브
WO2004099586A1 (fr) Soupape de commande, parties d'un turbocompresseur et systeme de suralimentation de turbocompresseur les comportant
US10316738B2 (en) Turbocharger engine
US9169906B2 (en) Link apparatus
US20140165561A1 (en) Supercharger Turbocharger Bypass Back Draft Inlet Damper for Series Operation
WO2021070463A1 (fr) Compresseur d'alimentation
US9243568B2 (en) Housing of a fresh gas supply device for an internal combustion engine and fresh gas supply device
WO2011072041A2 (fr) Soupape de recyclage de gaz d'échappement à basse pression
JP2009108773A (ja) エンジンシステム
JP2013019337A (ja) 多段過給システム
JP5967027B2 (ja) バタフライバルブ

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12803378

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12803378

Country of ref document: EP

Kind code of ref document: A1