EP1555421A2 - Abgasrückführeinrichtung einer Brennkraftmaschine - Google Patents

Abgasrückführeinrichtung einer Brennkraftmaschine Download PDF

Info

Publication number
EP1555421A2
EP1555421A2 EP05000942A EP05000942A EP1555421A2 EP 1555421 A2 EP1555421 A2 EP 1555421A2 EP 05000942 A EP05000942 A EP 05000942A EP 05000942 A EP05000942 A EP 05000942A EP 1555421 A2 EP1555421 A2 EP 1555421A2
Authority
EP
European Patent Office
Prior art keywords
gas
gas flow
elongate casing
passage
recirculation device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05000942A
Other languages
English (en)
French (fr)
Other versions
EP1555421A3 (de
EP1555421B1 (de
Inventor
Hiroyuki Komai
Masahiro Ariyama
Eriya Arita
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Filter Systems Japan Corp
Original Assignee
Mahle Filter Systems Japan Corp
Tennex Corp
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 Mahle Filter Systems Japan Corp, Tennex Corp filed Critical Mahle Filter Systems Japan Corp
Publication of EP1555421A2 publication Critical patent/EP1555421A2/de
Publication of EP1555421A3 publication Critical patent/EP1555421A3/de
Application granted granted Critical
Publication of EP1555421B1 publication Critical patent/EP1555421B1/de
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • F02M26/26—Layout, e.g. schematics with coolers having bypasses characterised by details of the bypass valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/04—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes comprising shape memory alloys or bimetallic elements

Definitions

  • the present invention relates in general to exhaust gas recirculation (viz., EGR) devices of an internal combustion engine, which feed part of the exhaust gas of the engine back to an intake side of the engine to reduce nitrogen oxides (NOx) in the exhaust gas, and more particularly to the EGR devices of a type that has a gas cooling means for cooling EGR gas.
  • EGR exhaust gas recirculation
  • the measures of the published applications have the following new drawbacks due to their inherent constructions. That is, in the former measure, the EGR device has a bulky construction causing a difficulty with which the EGR device is mounted to the engine, and in the latter measure, the EGR device fails to exhibit a satisfied ability for cooling EGR gas fed back to the engine.
  • an exhaust gas recirculation device of an internal combustion engine which can suitably control the temperature of EGR gas without enlarging the size of the device and sacrificing the gas cooling ability.
  • an exhaust gas recirculation device of an internal combustion engine which can control the temperature of EGR gas in accordance with an operation condition of the engine.
  • an exhaust gas recirculation device of an internal combustion engine which comprises a first elongate casing having gas inlet and outlet ports at axially opposed ends; a second elongate casing received in the first elongate casing to define therebetween an axially extending space, the second elongate casing including a first gas flow passage and a water flow passage that surrounds the first gas flow passage, the first gas flow passage having an inlet part exposed to the gas inlet port and an outlet part exposed to the gas outlet port; a third elongate casing received in the axially extending space to define between the first elongate casing and the third elongate casing a bypass passage and between the third elongate casing and the second elongate casing a second gas flow passage, the bypass passage and the second gas flow passage having each an inlet part exposed to the gas inlet port and an outlet part exposed to the gas outlet port; and a gas flow rate controller installed in either
  • an exhaust gas recirculation device of an internal combustion engine comprising a first elongate casing having gas inlet and outlet ports at axially opposed ends; a second elongate casing received in the first elongate casing to define therebetween an axially extending space, the second elongate casing including a first gas flow passage and a water flow passage that surrounds the first gas flow passage, the first gas flow passage having an inlet part exposed to the gas inlet port and an outlet part exposed to the gas outlet port; a third elongate casing received in the axially extending space to define between the first elongate casing and the third elongate casing a bypass passage and between the third elongate casing and the second elongate casing a second gas flow passage, the bypass passage and the second gas flow passage having each an inlet part exposed to the gas inlet port and an outlet part exposed to the gas outlet port; and a gas flow rate controller installed in the
  • an exhaust gas recirculation (EGR) device 100 which is a first embodiment of the present invention.
  • the EGR device 100 is arranged in an EGR piping that has an EGR gas inlet exposed to an interior of an exhaust passage of an associated internal combustion engine and an EGR gas outlet exposed to an interior of an air intake passage of the engine.
  • the EGR device 100 comprises a cylindrical housing (or first elongate casing) 1 that has inlet and outlet ports 2 and 3 at axially opposed ends thereof.
  • a cylindrical housing (or first elongate casing) 1 that has inlet and outlet ports 2 and 3 at axially opposed ends thereof.
  • respective flanges 4A and 4B To the inlet and outlet ports 2 and 3 of the housing 1, there are connected respective flanges 4A and 4B.
  • the flanges 4A and 4B are connected through bolts (not shown) to their counterparts (viz., flanges) of the piping.
  • soldering, welding, blazing and the like may be used for connecting the device 100 to the piping.
  • cylindrical casing 5 serves as a means for cooling EGR gas directed to the air intake passage of the engine.
  • the cylindrical casing 5 is of a double tube type including coaxially arranged inner and outer tubes 5a and 5b which have respective axial ends hermetically soldered to form therebetween a cylindrical water passage 6.
  • the inner and outer tubes 5a and 5b are constructed of a thin metal plate such as a stainless steel or the like.
  • the outer tube 5b has at axially opposed portions thereof respective openings (no numerals) to which water inlet and outlet pipes 7 and 8 are connected through soldering or the like. These water inlet and outlet pipes 7 and 8 are connected through respective tubes (not shown) to outlet and inlet portions of a source of a cooling water, such as a source of engine cooling water.
  • the cylindrical housing 1 has depressed apertures (no numerals) through which the water inlet and outlet pipes 7 and 8 extend radially outward. Under operation of the associated engine, the cooling water is led into the cylindrical water passage 6 through the water inlet pipe 7 and returned back to the source of the cooling water through the water outlet pipe 8. As will be described in detail hereinafter, during flowing of the cooling water in the cylindrical water passage 6, a heat exchanging is carried out between the cooling water and EGR gas flowing in and outside of the cylindrical casing 5.
  • a cylindrical partition tube (or third elongate casing) 9.
  • the partition tube 9 has portions (no numerals) secured to the water inlet and outlet pipes 7 and 8, so that the tube 9 is stably held in the housing 1. Due to provision of the cylindrical partition tube 9, there is defined a cylindrical bypass passage 10 between an inner surface of the cylindrical housing 1 and an outer surface of the cylindrical partition tube 9.
  • first gas cooling passage 11 that is cylindrical in shape
  • second gas cooling passage 12 that is cylindrical in shape
  • the bypass passage 10, the first gas cooling passage 11 and the second gas cooling passage 12 have respective inlet portions exposed to the inlet port 2 of the cylindrical housing 1 and respective outlet portions exposed to the outlet port 3 of the cylindrical housing 1.
  • each of the passages 10, 11 and 12 permits EGR gas to flow therein from the inlet port 2 toward the outlet port 3.
  • the inner tube 5a of the cylindrical case 5 has at its inner surface a plurality of heat exchanging fins 13 soldered thereto, and for the same reason between EGR gas in the second gas cooling passage 12 and the cooling water in the water passage 6, the outer tube 5b of the cylindrical case 5 is formed with a bellows or corrugated portion 14.
  • the respective apertured portions of the cylindrical housing 1, the cylindrical partition tube 9 and the outer tube 5b to which the water inlet or outlet pipe 7 or 8 is secured are intimately pressed and coupled to one another, so that the cylindrical casing 5 and the cylindrical partition tube 9 are tightly and stably held in the cylindrical housing 1.
  • a gas flow rate controller 15 that adjusts a gas flow rate among the bypass passage 10, the first gas cooling passage 11 and the second gas cooling passage 12.
  • the gas flow rate controller 15 is installed in the flange 4A connected to the inlet port 2 of the cylindrical housing 1.
  • the gas flow rate controller 15 comprises a pair of butterfly valves which are arranged in a parallel manner.
  • Each butterfly valve includes a pivot shaft 16a that extends perpendicular to an axis of the cylindrical housing 1, and a valve plate 16 that is secured to the pivot shaft 16a to pivot therewith.
  • the two pivot shafts 16a and 16a are symmetrically arranged with respect to the axis of the first gas cooling passage 11.
  • each valve plate 16 has a semicircular shape whose rounded outer periphery becomes in coincidence with the cylindrical inner surface of an inlet of the second gas cooling passage 12 when the valve plate 16 takes an inclined position (viz., the position shown by the dot-dash line) that will be described in the following.
  • FIGs. 2 and 3 there is shown an actuating mechanism for the gas flow rate controller 15. That is, the angular position of the valve plates 16 and 16 of the gas flow rate controller 15 is controlled by the actuating mechanism that is powered by a negative pressure produced in the intake passage of the engine.
  • the two pivot shafts 16a have extending portions that are exposed to the outside of the cylindrical housing 1.
  • each link mechanism 19 comprises a first link 19a having one end fixed to the pivot shaft 16a, and a second link 19b having one end pivotally connected to the other end of first link 19a through a pivot pin 19c.
  • the other ends of the second links 19b and 19b of the two link mechanisms 19 and 19 are pivotally connected through a pivot pin 19d to a plunger 18 of the actuator 17.
  • the actuator 17 is mounted to the outer surface of the cylindrical housing 1 and powered by a negative pressure produced in a throttle zone of the intake passage of the associated internal combustion engine.
  • the diaphragm type actuator 17 comprises generally a casing and a diaphragm installed in the casing to define therein a work chamber.
  • the diaphragm has the other end of the plunger 18 fixed thereto, and the work chamber is connected through a tube to the throttle zone of the intake passage of the engine.
  • a pressure controller is arranged in the tube so that the negative pressure applied to the actuator 17 is controlled in accordance with an operation condition of the engine.
  • an electric type actuator or a hydraulic type actuator may be used.
  • each valve plate 16 of the gas flow rate controller 15 is positioned and arranged to pivotally move the rounded outer periphery thereof in a limited zone that is defined in the inlet portion of the cylindrical housing 1 between the actual inlet of the bypass passage 10 and that of the cylindrical casing 5.
  • the pressure controller controls the negative pressure applied to the actuator 17 in such a manner that the valve plates 16 and 16 take their flat positions as shown by the solid line.
  • the EGR gas is led freely to all the bypass passage 10 and the first and second gas cooling passages 11 and 12.
  • heat exchanging is carried out between EGR gas and the cooling water in the water passage 6, and thus, the EGR gas directed to the air intake passage of the engine is suitably cooled.
  • this is advantageous for reducing nitrogen oxides (NOx) and particulates in the exhaust gas discharged from the engine.
  • the pressure controller arranged between the actuator 17 and the throttle zone of the intake passage of the engine is so constructed that the negative pressure applied to the actuator 17 is controlled in accordance with the operation condition of the engine.
  • the angular position of the two valve plates 16 and 16 that is, the rate between the amount of EGR gas flowing in both the first and second gas cooling passages 11 and 12 and the amount of EGR gas flowing in the bypass passage 10 is continuously controlled in accordance with the operation condition of the engine.
  • the temperature of EGR gas fed back to the intake passage of the engine can be suitably controlled in accordance with the engine operation condition.
  • the flow rate between the amount of EGR gas flowing in both the first and second gas cooling passages 11 and 12 and the amount of EGR gas flowing in the bypass passage 10 is optimally controlled.
  • the three gas flow passages 10, 11 and 12 and the cooling water passage 6 are defined by the three cylindrical members 1, 9 and 5 which are coaxially assembled.
  • the EGR device 100 can have a compact size, which is quite advantageous when mounting the device 100 to a limited space such as an engine room of current wheeled motor vehicles.
  • the valve plates 16 and 16 of the gas glow rate controller 15 are pivoted outward with respect to the axis of the cylindrical housing 1.
  • the valve plates 16 and 16 can serve as a guide means through which the EGR gas flow is smoothly guided toward the bypass passage 10.
  • the valve plates 16 and 16 are pivoted inward to take the flat positions that are in parallel with the axis of the cylindrical housing 1. In this case, the valve plates 16 and 16 have substantially no effect on the flowing of EGR gas in the first and second gas cooling passages 11 and 12.
  • the gas flow rate controller 15 is described to be arranged in the inlet port 2 of EGR device 100. However, if desired, such controller 15 may be arranged in the outlet port 3 of the device 100.
  • the gas flow rate controller 15 is described to be constructed to have the two valve plates 16 and 16. However, if desired, the gas flow rate controller 15 may have only one valve plate or more than two valve plates.
  • an exhaust gas recirculation (EGR) device 200 which is a second embodiment of the present invention.
  • EGR device 200 of this second embodiment is similar in construction to the EGR device 100 of the above-mentioned first embodiment, the following description on the second embodiment 200 will be directed to only parts or portions that are different from those of the first embodiment 100.
  • the water inlet and outlet pipes 7 and 8 are arranged to project radially outward from axially and diametrically opposite portions of the cylindrical housing 1.
  • the measures with which the water inlet or outlet pipe 7 or 8 is integrally connected to the depressed apertures of the cylindrical housing 1, the cylindrical partition tube 9 and the outer tube 5b of the cylindrical casing 5 are substantially the same as the measures mentioned in the first embodiment 100.
  • a slide-rotary type gas flow rate controller 115 is employed.
  • the flow rate controller 115 comprises a conical guide member 20 that is connected at its larger peripheral edge to an inlet edge of the cylindrical partition tube 9. Due to provision of a conical wall of the guide member 20, the EGR gas flow in the inlet port 2 toward the inlet of the bypass passage 10 is smoothly carried out.
  • the conical wall of the conical guide member 20 is formed with four identical sector openings 21 that are circumferentially arranged at evenly spaced intervals.
  • these openings 21 are kept open, the EGR gas in the inlet port 2 is permitted to flow toward the first and second gas cooling passages 11 and 12 through the openings 21.
  • a conical valve member 22 is coaxially and rotatably received in the conical guide member 20.
  • a conical wall of the conical valve member 22 is formed with four identical sector openings 23 that are circumferentially arranged at evenly spaced intervals and identical in shape and size to the four openings 21 of the above-mentioned conical guide member 20.
  • the conical valve member 22 has a center portion from which a control rod 24 extends axially outward (viz., leftward in the drawing) through a center opening (no numeral) of the conical guide member 20.
  • a leading end of the control rod 24 is connected to an actuator so that the control rod 24 is rotated about its axis in accordance with an operation condition of the associated internal combustion engine.
  • the gas flow rate controller 115 assumes a full-open position. While, when, due to turning of the conical valve member 22 to a second given angular position, the sector openings 23 of the conical valve member 22 are fully closed by a solid portion of the conical wall of the conical guide member 20, the gas flow rate controller 115 assumes a full-close position. Thus, when, due to turning of the control rod 24, the conical valve member 22 is turned between the first and second given angular positions, an open degree of the sector openings 21 of the conical guide member 20 is varied.
  • the EGR gas in the inlet port 2 can be smoothly led to the inlet of the bypass passage 10.
  • the flow rate controller 115 takes the full-close position, the sector openings 23 of the conical valve member 22 are fully and intimately closed by the solid part of the conical guide member 20.
  • almost all of EGR gas in the inlet port 2 can be led to the bypass passage 10. Due to the nature of the flow rate controller 115 of this slide - rotary type, undesired play, which would cause a noise in operation, is suppressed or at least minimized.
  • FIG. 6 there is shown an exhaust gas circulation (EGR) device 300 which is a third embodiment of the present invention.
  • EGR exhaust gas circulation
  • the EGR device 300 of this third embodiment is similar in construction to the EGR device 100 of the first embodiment, the following description on the third embodiment 300 will be directed to only parts or portions that are different from those of the first embodiment 100.
  • the water inlet and outlet pipes 7 and 8 are arranged to project radially outward from axially opposite and diametrically opposite portions of the cylindrical housing 1, like the above-mentioned second embodiment 200. Furthermore, the measures with which the water inlet or outlet pipe 7 or 8 is integrally connected to the depressed apertures of the cylindrical housing 1, the cylindrical partition tube 9 and the outer tube 5b of the cylindrical casing 5 are substantially the same as the measures mentioned in the first embodiment 100.
  • the inner tube 5a of the cylindrical case 5 is entirely formed with a bellows or corrugated portion 25 in place of the heat exchanging fins (13, see Fig. 1) of the first embodiment 100.
  • the outer tube 5b of the cylindrical case 5 is formed with the bellows or corrugated portion 14, like in the first and second embodiments 100 and 200.
  • a bimetal type gas flow rate controller 215 is used.
  • the flow rate controller 215 comprises a circular frame 31 that is fitted in the inlet port 2 of the cylindrical housing 1, and a pair of temperature sensitive valve plates 30 and 30 that are made of a bimetal material and have base ends held by the circular frame 31.
  • the valve plates 30 and 30 are made of a shape memory alloy.
  • Each valve plate 30 has a semicircular shape whose rounded outer periphery becomes in coincidence with the cylindrical inner surface of the inlet of the second gas cooling passage 12 when the valve plate 30 takes a largely bent position.
  • Denoted by numeral 32 is a conical gas inlet member that is fixed to the inlet port 2 of the cylindrical housing 1 for smoothing the flow of EGR gas toward the inlet port 2.
  • the temperature sensitive valve plates 30 and 30 take the generally flat positions as shown by the broken line.
  • the EGR gas is led to all the bypass passage 10 and the first and second gas cooling passages 11 and 12 as is described hereinabove.
  • heat exchanging is carried out between EGR gas and the cooling water in the water passage 6, and thus, the EGR gas directed to the air intake passage of the engine is suitable cooled.
  • the temperature sensitive valve plates 30 and 30 per se serve as an actuator.
  • this third embodiment 300 there is no need of using a separate actuator such as one that is actually used in the above-mentioned first and second embodiments 100 and 200.
  • a separate actuator such as one that is actually used in the above-mentioned first and second embodiments 100 and 200.
  • much compact, simple and light weight construction is expected in the EGR device 300 of this third embodiment.
  • the housing 1, the partition tube 9 and the casing 5 are described to have a cylindrical shape.
  • such members 1, 9 and 5 may be of a type that has a rectangular, pentagonal or other polygonal cross section.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP05000942A 2004-01-19 2005-01-18 Abgasrückführeinrichtung einer Brennkraftmaschine Ceased EP1555421B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004009960A JP4323333B2 (ja) 2004-01-19 2004-01-19 内燃機関の排気還流装置
JP2004009960 2004-01-19

Publications (3)

Publication Number Publication Date
EP1555421A2 true EP1555421A2 (de) 2005-07-20
EP1555421A3 EP1555421A3 (de) 2011-08-17
EP1555421B1 EP1555421B1 (de) 2013-03-13

Family

ID=34616928

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05000942A Ceased EP1555421B1 (de) 2004-01-19 2005-01-18 Abgasrückführeinrichtung einer Brennkraftmaschine

Country Status (3)

Country Link
EP (1) EP1555421B1 (de)
JP (1) JP4323333B2 (de)
CN (1) CN100439694C (de)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1672209A2 (de) * 2004-12-14 2006-06-21 Honeywell International, Inc. Bypass für abgaskühler
WO2006099965A1 (de) * 2005-03-19 2006-09-28 Daimlerchrysler Ag Luftansaugvorrichtung für eine brennkraftmaschine mit einsetzbarer bypassklappeneinrichtung
FR2891591A1 (fr) * 2005-09-30 2007-04-06 Renault Sas Dispositif de repartition des gaz recircules, et refroidisseur de gaz recircules comportant un tel dispositif
WO2007064949A1 (en) * 2005-12-02 2007-06-07 Borgwarner Inc. Combined egr valve and cooler by-pass
WO2007141435A1 (fr) * 2006-06-07 2007-12-13 Peugeot Citroën Automobiles SA Moteur a combustion interne ayant un circuit de recirculation des gaz d'echappement
WO2009022113A1 (en) * 2007-08-15 2009-02-19 Senior Uk Limited High gas inlet temperature egr system
DE102008005591A1 (de) * 2008-01-22 2009-07-23 Bayerische Motoren Werke Aktiengesellschaft Ventileinrichtung für eine Abgasrückführungseinrichtung
WO2009115975A2 (en) * 2008-03-17 2009-09-24 Dell'orto S.P.A. Egr valve for exhaust gas recirculation to the intake manifold of internal combustion engines
US7654078B2 (en) 2006-05-08 2010-02-02 Honeywell International, Inc. Exhaust gas particle collector
US7661415B2 (en) * 2004-09-28 2010-02-16 T.Rad Co., Ltd. EGR cooler
US7669645B2 (en) 2004-09-28 2010-03-02 T. Rad Co., Ltd. Heat exchanger
GB2490572A (en) * 2011-05-06 2012-11-07 Gm Global Tech Operations Inc A heat exchanger with temperature dependent coolant flow rate control
WO2014033075A1 (de) 2012-08-28 2014-03-06 Tenneco Gmbh Abgaswärmetauscher
WO2015155528A1 (en) * 2014-04-08 2015-10-15 Gt Precision Products Limited Dual valve actuator
GB2532177A (en) * 2014-06-04 2016-05-18 Norgren Ltd C A Exhaust gas control valve for an internal combustion engine
DE102012215221B4 (de) * 2011-09-01 2021-07-01 GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) Abgasrückführungssystem mit einem über aktives Material betätigten Bypass

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2322728B1 (es) * 2005-11-22 2010-04-23 Dayco Ensa, S.L. Intercambiador de calor de tres pasos para un sistema "egr".
DE102006023855A1 (de) * 2006-05-19 2007-11-22 Mahle International Gmbh Abgasrückführeinrichtung
US7581533B1 (en) * 2008-10-09 2009-09-01 Gm Global Technology Operations, Inc. Three mode cooler for exhaust gas recirculation
US20120067332A1 (en) * 2010-09-17 2012-03-22 Gm Global Technology Operations, Inc. Integrated exhaust gas recirculation and charge cooling system
JP5861865B2 (ja) * 2011-10-17 2016-02-16 大豊工業株式会社 Ｅｇｒクーラ
CN103306787B (zh) * 2013-06-17 2016-04-13 无锡创晨科技有限公司 水暖尾气加热器的滑桶式烟门开关装置
KR20150050921A (ko) * 2013-11-01 2015-05-11 현대중공업 주식회사 폐열 회수용 연관식 보일러
DE102014222158A1 (de) * 2014-10-30 2016-05-04 Mahle International Gmbh Abgaswärmeübertrager
CN113028858A (zh) * 2021-03-23 2021-06-25 中国航发沈阳发动机研究所 一种基于记忆合金的自适应换热器
CN113983852A (zh) * 2021-11-04 2022-01-28 浙江银轮机械股份有限公司 换热器壳体结构及换热器
CN113893953B (zh) * 2021-12-08 2022-02-25 苏州好博医疗器械股份有限公司 一种烟雾处理装置

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09508691A (ja) 1995-03-31 1997-09-02 カミンス エンジン カンパニー、インコーポレイテッド 負荷バイパス及び周囲バイパスを有する冷却排気再循環システム
JP2003328864A (ja) 2002-05-09 2003-11-19 Toyota Motor Corp 排気再循環装置及び排気再循環装置に用いられる熱交換器並びに内燃機関

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5740785A (en) * 1997-06-09 1998-04-21 Southwest Research Institute Two way-high pressure loop, exhaust gas recirculation valve
JP4009000B2 (ja) * 1998-02-24 2007-11-14 株式会社マーレ フィルターシステムズ 内燃機関のｅｇｒガスクーラ
JP2000282960A (ja) * 1999-03-31 2000-10-10 Nissan Diesel Motor Co Ltd Ｅｇｒ冷却装置
JP2001073883A (ja) * 1999-09-01 2001-03-21 Mitsubishi Motors Corp Ｅｇｒ装置
CN1167872C (zh) * 2000-06-20 2004-09-22 三菱电机株式会社 水冷式排气再循环装置
US6976480B2 (en) * 2002-01-16 2005-12-20 Mitsubishi Denki Kabushiki Kaisha Exhaust gas recirculating device
DE10203003B4 (de) * 2002-01-26 2007-03-15 Behr Gmbh & Co. Kg Abgaswärmeübertrager
CN100379971C (zh) * 2002-05-15 2008-04-09 贝洱两合公司 可控制的废气热交换器

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09508691A (ja) 1995-03-31 1997-09-02 カミンス エンジン カンパニー、インコーポレイテッド 負荷バイパス及び周囲バイパスを有する冷却排気再循環システム
JP2003328864A (ja) 2002-05-09 2003-11-19 Toyota Motor Corp 排気再循環装置及び排気再循環装置に用いられる熱交換器並びに内燃機関

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7854255B2 (en) 2004-09-28 2010-12-21 T. Rad Co., Ltd. Heat exchanger
US7661415B2 (en) * 2004-09-28 2010-02-16 T.Rad Co., Ltd. EGR cooler
US7669645B2 (en) 2004-09-28 2010-03-02 T. Rad Co., Ltd. Heat exchanger
US7694728B2 (en) 2004-09-28 2010-04-13 T. Rad Co., Ltd. Heat exchanger
EP1672209A3 (de) * 2004-12-14 2006-07-26 Honeywell International, Inc. Bypass für abgaskühler
US7198037B2 (en) 2004-12-14 2007-04-03 Honeywell International, Inc. Bypass for exhaust gas cooler
EP1672209A2 (de) * 2004-12-14 2006-06-21 Honeywell International, Inc. Bypass für abgaskühler
WO2006099965A1 (de) * 2005-03-19 2006-09-28 Daimlerchrysler Ag Luftansaugvorrichtung für eine brennkraftmaschine mit einsetzbarer bypassklappeneinrichtung
US7770563B2 (en) 2005-09-30 2010-08-10 Renault S.A.S. Device for distributing recirculated gases and recirculated gas-cooling device comprising one such device
WO2007039701A1 (fr) * 2005-09-30 2007-04-12 Renault S.A.S Dispositif de repartition des gaz recircules, et refroidisseur de gaz recircules comportant un tel dispositif
FR2891591A1 (fr) * 2005-09-30 2007-04-06 Renault Sas Dispositif de repartition des gaz recircules, et refroidisseur de gaz recircules comportant un tel dispositif
WO2007064949A1 (en) * 2005-12-02 2007-06-07 Borgwarner Inc. Combined egr valve and cooler by-pass
US7621128B2 (en) 2005-12-02 2009-11-24 Borgwarner Inc. Combined EGR valve and cooler by-pass
US7654078B2 (en) 2006-05-08 2010-02-02 Honeywell International, Inc. Exhaust gas particle collector
WO2007141435A1 (fr) * 2006-06-07 2007-12-13 Peugeot Citroën Automobiles SA Moteur a combustion interne ayant un circuit de recirculation des gaz d'echappement
FR2902151A1 (fr) * 2006-06-07 2007-12-14 Peugeot Citroen Automobiles Sa Moteur a combustion interne ayant un circuit de recirculation des gaz d'echappement
WO2009022113A1 (en) * 2007-08-15 2009-02-19 Senior Uk Limited High gas inlet temperature egr system
EP2570646A1 (de) * 2007-08-15 2013-03-20 Senior Uk Limited EGR-System mit hoher Gaseintrittstemperatur
DE102008005591A1 (de) * 2008-01-22 2009-07-23 Bayerische Motoren Werke Aktiengesellschaft Ventileinrichtung für eine Abgasrückführungseinrichtung
US8065992B2 (en) 2008-01-22 2011-11-29 Bayerische Motoren Werke Aktiengesellschaft Valve arrangement for an exhaust gas recirculation device
WO2009115975A2 (en) * 2008-03-17 2009-09-24 Dell'orto S.P.A. Egr valve for exhaust gas recirculation to the intake manifold of internal combustion engines
WO2009115975A3 (en) * 2008-03-17 2009-11-12 Dell'orto S.P.A. Egr valve for exhaust gas recirculation to the intake manifold of internal combustion engines
GB2490572B (en) * 2011-05-06 2016-08-24 Gm Global Tech Operations Llc Controllable heat exchanger for a motor vehicle air conditioning system
GB2490572A (en) * 2011-05-06 2012-11-07 Gm Global Tech Operations Inc A heat exchanger with temperature dependent coolant flow rate control
DE102012215221B4 (de) * 2011-09-01 2021-07-01 GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) Abgasrückführungssystem mit einem über aktives Material betätigten Bypass
WO2014033075A1 (de) 2012-08-28 2014-03-06 Tenneco Gmbh Abgaswärmetauscher
US9394813B2 (en) 2012-08-28 2016-07-19 Tenneco Gmbh Exhaust-gas heat exchanger
DE102012107908B4 (de) * 2012-08-28 2018-11-15 Tenneco Gmbh Abgaswärmetauscher
DE102012107908A1 (de) 2012-08-28 2014-03-06 Tenneco Gmbh Abgaswärmetauscher
WO2015155528A1 (en) * 2014-04-08 2015-10-15 Gt Precision Products Limited Dual valve actuator
GB2532177A (en) * 2014-06-04 2016-05-18 Norgren Ltd C A Exhaust gas control valve for an internal combustion engine

Also Published As

Publication number Publication date
CN1654807A (zh) 2005-08-17
CN100439694C (zh) 2008-12-03
JP4323333B2 (ja) 2009-09-02
JP2005201578A (ja) 2005-07-28
EP1555421A3 (de) 2011-08-17
EP1555421B1 (de) 2013-03-13

Similar Documents

Publication Publication Date Title
EP1555421B1 (de) Abgasrückführeinrichtung einer Brennkraftmaschine
US8695332B2 (en) Internal bypass exhaust gas cooler
JP6186276B2 (ja) バイパスを備える排熱回収装置
CA2474065C (en) Exhaust gas heat exchanger
US7931013B2 (en) Three-pass heat exchanger for an EGR system
JP5380522B2 (ja) マルチポート弁
EP1859156B1 (de) Bypass- und abgasrezirkulationsventil
KR20020031052A (ko) 차량의 냉각 시스템
EP1426604A2 (de) Strömungswegumschaltventil
EP1605145B1 (de) Abgassystem einer mehrzylindrigen Brennkraftmaschine
US20090241527A1 (en) Arrangement for cooling the exhaust gas of a motor vehicle
JP4732157B2 (ja) 切替バルブ構造
JP2020041535A (ja) 制御バルブ
JP6247357B2 (ja) タービンハウジング
JP2019065795A (ja) 内燃機関
JP2007224784A (ja) 内燃機関用シリンダヘッド
CN210135111U (zh) 压缩机及涡轮增压器
EP3090161B1 (de) Turbolader mit verbesserter bypass-ventildichtung
JP6459632B2 (ja) 内燃機関用吸排気装置
JP2020200828A (ja) 弁、内燃機関用の排気分岐体、及び内燃機関を備えた車両
JP2563930Y2 (ja) エンジン用マフラーのバルブ構造
EP1923550A2 (de) Bypassbaugruppe für einen Systemluftkühler
JP2024093570A (ja) 排気熱回収器
JPS6196117A (ja) 可変消音器
JP2539442Y2 (ja) 内燃機関用消音器

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR LV MK YU

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAHLE FILTER SYSTEMS JAPAN CORPORATION

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR LV MK YU

RIC1 Information provided on ipc code assigned before grant

Ipc: F02M 25/07 20060101AFI20110714BHEP

17P Request for examination filed

Effective date: 20110908

AKX Designation fees paid

Designated state(s): DE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602005038521

Country of ref document: DE

Effective date: 20130508

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20131216

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602005038521

Country of ref document: DE

Effective date: 20131216

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140128

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602005038521

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150801