EP1555421A2 - Exhaust gas recirculation device of internal combustion engine - Google Patents
Exhaust gas recirculation device of internal combustion engine Download PDFInfo
- 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.)
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Classifications
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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.
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- 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)
Abstract
Description
- 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.
- Hitherto, various EGR devices of an internal combustion engine have been proposed and put into practical use particularly in the field of wheeled motor vehicles. Some of them are of a gas cooling type that has a means for cooling EGR gas to achieve an efficient feeding of the EGR gas, which has been thermally expanded, to an intake side of the engine. However, in case just after engine starting wherein the engine temperature is low and/or under a low load operation of the engine, such cooling of EGR gas is not preferable. Actually, in such cases of the engine, the cooling of EGR gas tends to cause increase of particulates as well as nitrogen oxides (NOx) in the exhaust gas discharged from the engine.
- For solving such drawbacks, measures are proposed by two Japanese Laid-open Patent Applications which are Tokuhyohei-9-508691 and Tokkai-2003-328864. In the former measure, a bypass passage is provided outside of a gas cooling passage. In the latter measure, a bypass passage is provided inside of a gas cooling passage like a nest. In both measures, when the gas cooling is not necessary, the EGR gas is fed back to the intake side of the engine through the bypass passage.
- However, even 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.
- It is therefore an object of the present invention to provide an exhaust gas recirculation device of an internal combustion engine, which is free of the above-mentioned drawbacks.
- That is, according to the present invention, there is provided 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.
- More specifically, according to the present invention, there is provided 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.
- In accordance with a first aspect of the present invention, there is provided 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 one of the gas inlet and outlet ports of the first elongate casing to control a gas flow rate among the bypass passage, the first gas flow passage and the second gas flow passage.
- In accordance with a second aspect of the present invention, there is provided 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 gas inlet port of the first elongate casing to control a rate between the amount of gas flowing in both the first and second gas flow passages and the amount of gas flowing in the bypass passage.
- Other objects and advantages of the present invention will become apparent from the following description when taken in conjunction with the accompanying drawings, in which:
- Fig. 1 is a sectional view of an exhaust gas recirculation device which is a first embodiment of the present invention;
- Fig. 2 is a view taken from the direction of the arrow "A" of Fig. 1;
- Fig. 3 is a side view of the exhaust gas recirculation device of the first embodiment;
- Fig. 4 is a view similar to Fig. 1, but showing an exhaust gas recirculation device of a second embodiment of the present invention;
- Fig. 5 is a view taken from the direction of the arrow "B" of Fig. 4; and
- Fig. 6 is a view similar to Fig. 1, but showing an exhaust gas recirculation device of a third embodiment of the present invention.
-
- In the following, three
embodiments - For ease of understanding, various directional terms, such as, right, left, upper, lower, rightward and the like are used in the following description. However, such terms are to be understood with respect to only a drawing or drawings on which a corresponding part or portion is shown.
- Referring to Figs. 1 to 3 of the drawings, there is shown an exhaust gas recirculation (EGR)
device 100 which is a first embodiment of the present invention. - Although not shown in the drawings, 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. - As is well seen from Fig. 1, the
EGR device 100 comprises a cylindrical housing (or first elongate casing) 1 that has inlet andoutlet ports outlet ports housing 1, there are connectedrespective flanges flanges device 100 to the piping. - Within the
cylindrical housing 1, there is coaxially disposed a cylindrical casing (or second elongate casing) 5. As will become apparent hereinafter, thecylindrical 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 andouter tubes cylindrical water passage 6. Preferably, the inner andouter tubes - As shown in Fig. 1, the
outer tube 5b has at axially opposed portions thereof respective openings (no numerals) to which water inlet andoutlet pipes outlet pipes cylindrical housing 1 has depressed apertures (no numerals) through which the water inlet andoutlet pipes cylindrical water passage 6 through thewater inlet pipe 7 and returned back to the source of the cooling water through thewater outlet pipe 8. As will be described in detail hereinafter, during flowing of the cooling water in thecylindrical water passage 6, a heat exchanging is carried out between the cooling water and EGR gas flowing in and outside of thecylindrical casing 5. - As shown, between the
cylindrical housing 1 and thecylindrical casing 5, there is coaxially arranged a cylindrical partition tube (or third elongate casing) 9. Thepartition tube 9 has portions (no numerals) secured to the water inlet andoutlet pipes tube 9 is stably held in thehousing 1. Due to provision of thecylindrical partition tube 9, there is defined acylindrical bypass passage 10 between an inner surface of thecylindrical housing 1 and an outer surface of thecylindrical partition tube 9. - In the
cylindrical casing 5, there is defined a firstgas cooling passage 11 that is cylindrical in shape, and between an inner surface of thecylindrical partition tube 9 and an outer surface of the cylindrical casing 5 (more specifically, theouter tube 5b), there is defined a secondgas cooling passage 12 that is cylindrical in shape. - As shown in Fig. 1, the
bypass passage 10, the firstgas cooling passage 11 and the secondgas cooling passage 12 have respective inlet portions exposed to theinlet port 2 of thecylindrical housing 1 and respective outlet portions exposed to theoutlet port 3 of thecylindrical housing 1. Thus, each of thepassages inlet port 2 toward theoutlet port 3. - As is understood from the drawing, only EGR gas flowing in the first and second
gas cooling passages water passage 6 of thecylindrical casing 5. That is, the EGR gas flowing in thebypass passage 10 is not permitted to carry out such heat exchanging with the cooling water in thewater passage 6. - For improving the heat exchanging between EGR gas in the first
gas cooling passage 11 and the cooling water in thewater passage 6, theinner tube 5a of thecylindrical 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 secondgas cooling passage 12 and the cooling water in thewater passage 6, theouter tube 5b of thecylindrical case 5 is formed with a bellows orcorrugated portion 14. - As shown, the respective apertured portions of the
cylindrical housing 1, thecylindrical partition tube 9 and theouter tube 5b to which the water inlet oroutlet pipe cylindrical casing 5 and thecylindrical partition tube 9 are tightly and stably held in thecylindrical housing 1. - In the
cylindrical housing 1 near theinlet port 2, there is arranged a gasflow rate controller 15 that adjusts a gas flow rate among thebypass passage 10, the firstgas cooling passage 11 and the secondgas cooling passage 12. - As is understood from Figs. 1, 2 and 3, the gas
flow rate controller 15 is installed in theflange 4A connected to theinlet port 2 of thecylindrical housing 1. - As is seen from Figs. 1 and 2, the gas
flow rate controller 15 comprises a pair of butterfly valves which are arranged in a parallel manner. Each butterfly valve includes apivot shaft 16a that extends perpendicular to an axis of thecylindrical housing 1, and avalve plate 16 that is secured to thepivot shaft 16a to pivot therewith. As is seen from the drawings, the twopivot shafts gas cooling passage 11. - As is understood from Figs. 1 and 2, 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 secondgas cooling passage 12 when thevalve plate 16 takes an inclined position (viz., the position shown by the dot-dash line) that will be described in the following. - As is seen from Fig. 1, when the
valve plates bypass passage 10 and the first and secondgas cooling passages valve plates valve plates gas cooling passages bypass passage 10. As is seen from the drawing, when thevalve plates valve plates valve plates - Referring to Figs. 2 and 3, there is shown an actuating mechanism for the gas
flow rate controller 15. That is, the angular position of thevalve plates 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. - As is seen from Fig. 2, the two
pivot shafts 16a have extending portions that are exposed to the outside of thecylindrical housing 1. - As is seen from Fig. 3, the exposed extending portions of the
pivot shafts 16a are actuated by adiaphragm type actuator 17 throughrespective link mechanisms - That is, each
link mechanism 19 comprises afirst link 19a having one end fixed to thepivot shaft 16a, and asecond link 19b having one end pivotally connected to the other end offirst link 19a through apivot pin 19c. The other ends of thesecond links link mechanisms pivot pin 19d to aplunger 18 of theactuator 17. Theactuator 17 is mounted to the outer surface of thecylindrical housing 1 and powered by a negative pressure produced in a throttle zone of the intake passage of the associated internal combustion engine. - Although not well shown in the drawings, 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 theplunger 18 fixed thereto, and the work chamber is connected through a tube to the throttle zone of the intake passage of the engine. Although not shown in the drawing, a pressure controller is arranged in the tube so that the negative pressure applied to theactuator 17 is controlled in accordance with an operation condition of the engine. - In place of the
diaphragm type actuator 17, an electric type actuator or a hydraulic type actuator may be used. - Referring back to Fig. 1, the actual inlet of the
bypass passage 10 is positioned much closer to theinlet port 2 of thecylindrical housing 1 than that of thecylindrical casing 5 is positioned. As is seen from this drawing, eachvalve plate 16 of the gasflow 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 thecylindrical housing 1 between the actual inlet of thebypass passage 10 and that of thecylindrical casing 5. - When the associated engine is in operation keeping its temperature relatively high, the pressure controller controls the negative pressure applied to the
actuator 17 in such a manner that thevalve plates bypass passage 10 and the first and secondgas cooling passages gas cooling passages water passage 6, and thus, the EGR gas directed to the air intake passage of the engine is suitably cooled. As is described hereinabove, this is advantageous for reducing nitrogen oxides (NOx) and particulates in the exhaust gas discharged from the engine. - While, when, like in case just after engine starting, the engine temperature is relatively low, the pressure controller controls the negative pressure applied to the
actuator 17 in such a manner that thevalve plates bypass passage 10 bypassing the first and secondgas cooling passages gas cooling passage 12 serves as a heat insulating layer and thus the EGR gas flowing in thebypass passage 10 is not affected or cooled by the cooling water in thewater passage 6. Thus, ironical increase of nitrogen oxides (NOx) and particulates in the exhaust gas, which would occur when the engine temperature is low, is suppressed or at least minimized. - As is described hereinabove, 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. This means that the angular position of the twovalve plates gas cooling passages bypass passage 10 is continuously controlled in accordance with the operation condition of the engine. Thus, 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. - As is mentioned hereinabove, by operating the gas
flow rate controller 15 of theEGR device 100 in accordance with the engine operation condition, the flow rate between the amount of EGR gas flowing in both the first and secondgas cooling passages bypass passage 10 is optimally controlled. - In the
EGR device 100, the threegas flow passages water passage 6 are defined by the threecylindrical members EGR device 100 can have a compact size, which is quite advantageous when mounting thedevice 100 to a limited space such as an engine room of current wheeled motor vehicles. - In the
EGR device 100, in case of reducing EGR gas flow in the first and secondgas cooling passages 11 and 12 (that is, in case of increasing EGR gas flow in the bypass passage 10), thevalve plates glow rate controller 15 are pivoted outward with respect to the axis of thecylindrical housing 1. In this case, thevalve plates bypass passage 10. While, in case of increasing EGR gas flow in the first and secondgas cooling passages 11 and 12 (that is, in case of reducing EGR gas flow in the bypass passage 10), thevalve plates cylindrical housing 1. In this case, thevalve plates gas cooling passages - In the foregoing description, the gas
flow rate controller 15 is described to be arranged in theinlet port 2 ofEGR device 100. However, if desired,such controller 15 may be arranged in theoutlet port 3 of thedevice 100. - In the foregoing description, the gas
flow rate controller 15 is described to be constructed to have the twovalve plates flow rate controller 15 may have only one valve plate or more than two valve plates. - Referring to Figs. 4 and 5, there is shown an exhaust gas recirculation (EGR)
device 200 which is a second embodiment of the present invention. - Since the
EGR device 200 of this second embodiment is similar in construction to theEGR device 100 of the above-mentioned first embodiment, the following description on thesecond embodiment 200 will be directed to only parts or portions that are different from those of thefirst embodiment 100. - As shown in Fig. 4, in this
second embodiment 200, the water inlet andoutlet pipes cylindrical housing 1. As shown, the measures with which the water inlet oroutlet pipe cylindrical housing 1, thecylindrical partition tube 9 and theouter tube 5b of thecylindrical casing 5 are substantially the same as the measures mentioned in thefirst embodiment 100. - As is seen from Fig. 4, in this
second embodiment 200, a slide-rotary type gasflow rate controller 115 is employed. - That is, the
flow rate controller 115 comprises aconical guide member 20 that is connected at its larger peripheral edge to an inlet edge of thecylindrical partition tube 9. Due to provision of a conical wall of theguide member 20, the EGR gas flow in theinlet port 2 toward the inlet of thebypass passage 10 is smoothly carried out. - As is seen from Figs. 4 and 5, particularly Fig. 5, the conical wall of the
conical guide member 20 is formed with fouridentical sector openings 21 that are circumferentially arranged at evenly spaced intervals. Thus, when, as is seen from Fig. 4, theseopenings 21 are kept open, the EGR gas in theinlet port 2 is permitted to flow toward the first and secondgas cooling passages openings 21. - Referring back to Fig. 4, a
conical valve member 22 is coaxially and rotatably received in theconical guide member 20. - As is seen from Figs. 4 and 5, particularly Fig. 5, a conical wall of the
conical valve member 22 is formed with fouridentical sector openings 23 that are circumferentially arranged at evenly spaced intervals and identical in shape and size to the fouropenings 21 of the above-mentionedconical guide member 20. - As is seen from Fig. 4, the
conical valve member 22 has a center portion from which acontrol rod 24 extends axially outward (viz., leftward in the drawing) through a center opening (no numeral) of theconical guide member 20. Although not shown in the drawing, a leading end of thecontrol rod 24 is connected to an actuator so that thecontrol rod 24 is rotated about its axis in accordance with an operation condition of the associated internal combustion engine. - When, due to turning of the
conical valve member 22 to a first given angular position, thesector openings 23 of theconical valve member 22 become in coincidence with thesector openings 21 of theconical guide member 20, the gasflow rate controller 115 assumes a full-open position. While, when, due to turning of theconical valve member 22 to a second given angular position, thesector openings 23 of theconical valve member 22 are fully closed by a solid portion of the conical wall of theconical guide member 20, the gasflow rate controller 115 assumes a full-close position. Thus, when, due to turning of thecontrol rod 24, theconical valve member 22 is turned between the first and second given angular positions, an open degree of thesector openings 21 of theconical guide member 20 is varied. - In the
EGR device 200 of this second embodiment, due to provision of theconical guide member 20, the EGR gas in theinlet port 2 can be smoothly led to the inlet of thebypass passage 10. When theflow rate controller 115 takes the full-close position, thesector openings 23 of theconical valve member 22 are fully and intimately closed by the solid part of theconical guide member 20. Thus, in this condition, almost all of EGR gas in theinlet port 2 can be led to thebypass passage 10. Due to the nature of theflow rate controller 115 of this slide - rotary type, undesired play, which would cause a noise in operation, is suppressed or at least minimized. - Referring to Fig. 6, there is shown an exhaust gas circulation (EGR)
device 300 which is a third embodiment of the present invention. - Since, like the above-mentioned
second embodiment 200, theEGR device 300 of this third embodiment is similar in construction to theEGR device 100 of the first embodiment, the following description on thethird embodiment 300 will be directed to only parts or portions that are different from those of thefirst embodiment 100. - As is seen from Fig. 6, in this
third embodiment 300, the water inlet andoutlet pipes cylindrical housing 1, like the above-mentionedsecond embodiment 200. Furthermore, the measures with which the water inlet oroutlet pipe cylindrical housing 1, thecylindrical partition tube 9 and theouter tube 5b of thecylindrical casing 5 are substantially the same as the measures mentioned in thefirst embodiment 100. - As is understood from the drawing, in the
EGR device 300 of the third embodiment, theinner tube 5a of thecylindrical case 5 is entirely formed with a bellows orcorrugated portion 25 in place of the heat exchanging fins (13, see Fig. 1) of thefirst embodiment 100. Theouter tube 5b of thecylindrical case 5 is formed with the bellows orcorrugated portion 14, like in the first andsecond embodiments - As is seen from the drawing, in this
third embodiment 300, a bimetal type gasflow rate controller 215 is used. - That is, the
flow rate controller 215 comprises acircular frame 31 that is fitted in theinlet port 2 of thecylindrical housing 1, and a pair of temperaturesensitive valve plates circular frame 31. Preferably, thevalve plates - 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 secondgas cooling passage 12 when thevalve plate 30 takes a largely bent position. Denoted bynumeral 32 is a conical gas inlet member that is fixed to theinlet port 2 of thecylindrical housing 1 for smoothing the flow of EGR gas toward theinlet port 2. - As is seen from the drawing, when the
valve plates bypass passage 10 and the first and secondgas cooling passages valve plates valve plates gas cooling passages bypass passage 10. - When the associated engine is in operation keeping its temperature relatively high, the temperature of the exhaust gas discharged from the engine is relatively high, and thus, the temperature of EGR gas directed toward the
EGR device 300 is relatively high. Under this condition, the temperaturesensitive valve plates bypass passage 10 and the first and secondgas cooling passages gas cooling passages water passage 6, and thus, the EGR gas directed to the air intake passage of the engine is suitable cooled. - While, when, like in case just after engine starting, the engine temperature is relatively low, the temperature of the exhaust gas discharged from the engine is relatively low and thus, the temperature of EGR gas directed toward the
EGR device 300 is relatively low. Under this condition, the temperaturesensitive valve plates bypass passage 10 bypassing the first and secondgas cooling passages - In the EGR device of this
third embodiment 300, the temperaturesensitive valve plates third embodiment 300, there is no need of using a separate actuator such as one that is actually used in the above-mentioned first andsecond embodiments EGR device 300 of this third embodiment. - In the foregoing explanation, the
housing 1, thepartition tube 9 and thecasing 5 are described to have a cylindrical shape. However, if desired,such members - The entire contents of Japanese Patent Application 2004-009960 filed January 19, 2004 are incorporated herein by reference.
- Although the invention has been described above with reference to the embodiments of the invention, the invention is not limited to such embodiments as described above. Various modifications and variations of such embodiments may be carried out by those skilled in the art, in light of the above description.
Claims (20)
- 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; anda gas flow rate controller installed in either one of the gas inlet and outlet ports of the first elongate casing to control a gas flow rate among the bypass passage, the first gas flow passage and the second gas flow passage.
- An exhaust gas recirculation device as claimed in Claim 1, in which the gas flow rate controller is constructed to control the rate between the amount of gas flowing in both the first and second gas flow passages and the amount of gas flowing in the bypass passage.
- An exhaust gas recirculation device as claimed in Claim 1, in which the gas flow rate controller is installed in the gas inlet port of the first elongate casing and comprises:a valve member that is movable between a first position wherein the gas flow from the inlet port toward the bypass passage, the first gas flow passage and the second gas flow passage is freely carried out without being obstructed by the valve plate and a second position wherein the gas flow from the inlet port toward the first and second gas flow passages is reduced as compared with the gas flow from the inlet port toward the bypass passage.
- An exhaust gas recirculation device as claimed in Claim 3, further comprising an actuating mechanism that continuously moves the valve member between the first and second positions.
- An exhaust gas recirculation device as claimed in Claim 4, in which the valve member comprises:a pair of pivot shafts arranged in the inlet port in a parallel manner; anda pair of valve plates secured respectively to the pivot shafts to pivot therewith,
- An exhaust gas recirculation device as claimed in Claim 5, in which the actuating mechanism comprises:an actuator mounted to the first elongate casing; anda pair of link mechanisms, each being operatively interposed between the actuator and corresponding one of the pivot shafts.
- An exhaust gas recirculation device as claimed in Claim 6, in which the actuator is a diaphragm type actuator powered by a negative pressure produced in a throttle zone of an intake passage of the engine.
- An exhaust gas recirculation device as claimed in Claim 6, in which each of the link mechanisms comprises:a first link having one end fixed to corresponding one of the pivot shafts;a second link having one end pivotally connected to the other end of the first link and the other end pivotally connected to a plunger of the actuator.
- An exhaust gas recirculation device as claimed in Claim 1, in which the second elongate casing is of a double tube type comprising coaxially arranged inner and outer tubes which have respective axial ends to form therebetween the water flow passage, the inner tube defining therein the first gas flow passage.
- An exhaust gas recirculation device as claimed in Claim 9, in which the inner tube is formed with heat exchanging means, and in which the outer tube is formed with a bellows or corrugated portion.
- An exhaust gas recirculation device as claimed in Claim 10, in which the heat exchanging means is one of a plurality of fins soldered to an inner surface of the inner tube and a bellows or corrugated portion formed on the inner tube.
- An exhaust gas recirculation device as claimed in Claim 1, further comprising water inlet and outlet pipes each having an inner end exposed to the water flow passage of the second elongate casing.
- An exhaust gas recirculation device as claimed in Claim 12, in which the water inlet and outlet pipes are arranged at axially opposed and diametrically same positions of the first elongate casing.
- An exhaust gas recirculation device as claimed in Claim 12, in which the water inlet and outlet pipes are arranged at axially opposed and diametrically opposed positions of the first elongate casing.
- An exhaust gas recirculation device as claimed in Claim 4, in which the gas flow rate controller comprises:a conical guide member secured to the third elongate casing, the conical guide member being formed at a conical wall thereof with a plurality of first openings;a conical valve member coaxially and rotatably received in the conical guide member, the conical valve member being formed at a conical wall thereof with a plurality of second openings, the conical valve member being turned between an open position wherein the first and second openings are mated and a close position wherein the first and second openings are not mated; anda control rod having one end that passes through a center opening of the conical guide member to be secured to a center portion of the conical valve member, the control rod having the other end connected to the actuator.
- An exhaust gas recirculation device as claimed in Claim 15, in which the conical wall of the conical guide member is arranged to smooth EGR gas flow from the gas inlet port of the first elongate casing toward an inlet of the bypass passage.
- An exhaust gas recirculation device as claimed in Claim 4, in which gas flow rate controller comprises:a frame member fitted in the gas inlet port of the first elongate casing; anda pair of thermally sensitive valve plates, each having a base end that is held by the frame member and a free portion that shows a deformation when applied with a heat, the free portion being flexed by the heat between a first position wherein the gas flow from the gas inlet port toward the bypass passage, the first gas flow passage and the second gas flow passage is freely carried out without being obstructed by the valve plates and a second position wherein the gas flow from the gas inlet port toward the first and second gas flow passages is reduced as compared with the gas flow from the gas inlet port toward the bypass passage,
- An exhaust gas recirculation device as claimed in Claim 17, in which the thermally sensitive valves plates are constructed of a bimetal or a shape memory alloy.
- An exhaust gas recirculation device as claimed in Claim 18, further comprising a conical gas inlet member that is fixed to the gas inlet port of the first elongate casing to smooth the gas flow toward the gas inlet port.
- 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; anda gas flow rate controller installed in the gas inlet port of the first elongate casing to control a rate between the amount of gas flowing in both the first and second gas flow passages and the amount of gas flowing in the bypass passage.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004009960 | 2004-01-19 | ||
JP2004009960A JP4323333B2 (en) | 2004-01-19 | 2004-01-19 | Exhaust gas recirculation device for internal combustion engine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1555421A2 true EP1555421A2 (en) | 2005-07-20 |
EP1555421A3 EP1555421A3 (en) | 2011-08-17 |
EP1555421B1 EP1555421B1 (en) | 2013-03-13 |
Family
ID=34616928
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05000942A Expired - Fee Related EP1555421B1 (en) | 2004-01-19 | 2005-01-18 | Exhaust gas recirculation device of internal combustion engine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1555421B1 (en) |
JP (1) | JP4323333B2 (en) |
CN (1) | CN100439694C (en) |
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WO2007064949A1 (en) * | 2005-12-02 | 2007-06-07 | Borgwarner Inc. | Combined egr valve and cooler by-pass |
WO2007141435A1 (en) * | 2006-06-07 | 2007-12-13 | Peugeot Citroën Automobiles SA | Internal combustion engine comprising an exhaust gas recirculation system |
WO2009022113A1 (en) * | 2007-08-15 | 2009-02-19 | Senior Uk Limited | High gas inlet temperature egr system |
DE102008005591A1 (en) * | 2008-01-22 | 2009-07-23 | Bayerische Motoren Werke Aktiengesellschaft | Valve device 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 |
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US7661415B2 (en) * | 2004-09-28 | 2010-02-16 | T.Rad Co., Ltd. | EGR cooler |
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Also Published As
Publication number | Publication date |
---|---|
EP1555421B1 (en) | 2013-03-13 |
CN100439694C (en) | 2008-12-03 |
JP2005201578A (en) | 2005-07-28 |
JP4323333B2 (en) | 2009-09-02 |
CN1654807A (en) | 2005-08-17 |
EP1555421A3 (en) | 2011-08-17 |
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