JP2014185618A - Exhaust gas recirculation device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an exhaust gas recirculation device (9) for recirculating exhaust gas from exhaust passages (52, 53) into an intake system 4, in which water vapor mixed in the exhaust gas is condensed and the condensed water is hardly caused to flow into the intake system 4, independently of the operating condition of an internal combustion engine 1.SOLUTION: The exhaust gas recirculation device (9) includes a condenser 11 for condensing the water vapor contained in the exhaust gas passing through an EGR valve 92, a condensed water reservoir 13 for reserving water to be condensed by the condenser 11. The condenser 11 is arranged on the further vertically lower side than the EGR valve 92, and installed in such an attitude that it is located at its exhaust gas introduction side on the further vertically upper side than its exhaust side. The condensed water reservoir 13 is arranged on the further downstream side in an exhaust gas flowing direction than the condenser 11 and on the further vertically lower side than the condenser 11. An EGR passage 91 in a region from the condensed water reservoir 13 to the intake system 4 has an attitude to be vertically upward from the side of the condensed water reservoir 13 to the side of the intake system 4.

Description

  The present invention relates to an exhaust gas recirculation device for recirculating exhaust gas discharged from an internal combustion engine (engine) into an exhaust passage to an intake system.

  An engine mounted on a vehicle is equipped with an exhaust gas recirculation (EGR) device that is effective in reducing NOx (nitrogen oxide) (see, for example, Patent Document 1).

  In this EGR device, the condensed water generated by cooling the exhaust gas in the EGR cooler is separated from the exhaust gas, and the condensed water is stored in the tank, while the exhaust gas is sent to the intake system. doing.

  For example, Patent Document 2 describes that a turbocharged engine is equipped with an HPL (High Pressure Loop) -EGR device and an LPL (Low Pressure Loop) -EGR device.

  Since the recirculated exhaust gas of the LPL-EGR device is lower in pressure and temperature than the recirculated exhaust gas of the HPL-EGR device, it becomes easier to generate acidic condensed water by being cooled by the EGR cooler. The condensed water is adsorbed and held by the water absorbing material installed downstream of the filter portion in the exhaust gas flow direction in the exhaust gas passage in the DPF unit, and the condensed water of the water absorbing material is evaporated by the high temperature exhaust gas. I try to let them.

JP-A-7-269417 JP2012-202265A

  In Patent Document 1, condensed water is generated in the EGR cooler. However, when the EGR cooler is controlled to be in a cooling state that does not generate condensed water, the EGR cooler is located downstream of the EGR cooler. There is concern that condensed water is generated in the intake system passage and is likely to flow into the combustion chamber of the internal combustion engine.

  In Patent Document 2, the condensed water generated in the LPL-EGR device is evaporated while adsorbed and held by the water absorbing material, but is not discharged to the outside. If the state where the state is such that the exhaust gas is discharged at a relatively low temperature is continued, it is difficult to evaporate the condensed water adsorbed and retained by the water absorbing material. There is a risk of flowing into the intake system together with the exhaust gas due to wind pressure. There is room for improvement here.

  In view of such circumstances, the present invention provides an exhaust gas recirculation device for recirculating exhaust gas discharged from an internal combustion engine to an exhaust passage to an intake system, and is configured to remove water vapor mixed in the exhaust gas during operation of the internal combustion engine. It is intended to condense and prevent the condensed water from flowing into the intake system.

  The present invention relates to an exhaust gas recirculation device for recirculating exhaust gas discharged from an internal combustion engine to an exhaust passage to an intake system, an EGR passage that connects the exhaust passage and the intake system, and an EGR passage. EGR cooler for cooling exhaust gas to be introduced, EGR valve for opening and closing the outlet of this EGR cooler, condensing device for condensing water vapor contained in exhaust gas passing through this EGR valve, and this condensing device A condensate water reservoir for storing water condensed in the exhaust gas, wherein the condensing device is disposed below the EGR valve in the vertical direction and the exhaust gas introduction side is located above the discharge side in the vertical direction. The condensate pool is disposed downstream of the condensing device in the exhaust flow direction and vertically below the condensing device, and the E Region of the R channel from the condensing pools to the intake system is the posture to be vertically upward direction from the condensing puddles side to the intake system side, it is characterized in that.

  In this configuration, when the high-temperature exhaust gas discharged from the internal combustion engine is cooled by the EGR cooler and then introduced into the condensing device during the operation of the internal combustion engine, the water vapor mixed in the exhaust gas Is condensed by being cooled to its dew point temperature. The condensed moisture is stored in the condensed water reservoir disposed vertically below the condensing device, while the exhaust gas from which the water vapor has been removed passes through the condensed water reservoir and The air flows into the intake system through the communication path.

  Thus, by specifying the relative position in the vertical direction in the condensing device, the condensate pool, the connection portion of the EGR passage with the intake system, etc., the water vapor mixed in the exhaust gas is efficiently condensed. By dropping this condensed water into the condensed water reservoir, the condensed water is hardly transported to the intake system by the wind pressure of the exhaust gas.

  As a result, metal parts (valves and the like) existing in the intake system can be prevented from being corroded by the condensed water, and the condensed water can be prevented from entering the combustion chamber of the internal combustion engine. It becomes possible to avoid a hammer phenomenon and a misfire phenomenon. Further, in the above configuration, the condensed water does not accumulate in the EGR cooler as compared with the case where the water vapor mixed in the exhaust gas is condensed only by the EGR cooler, so that the EGR cooler can be corroded or damaged by the condensed water. Low.

  Preferably, the condensate pool may be provided with a drain passage for discharging the water stored therein to the outside.

  In this configuration, it is possible to avoid the occurrence of a problem that the condensed water reservoir corrodes and opens a hole, as in the case where the water condensed in the condenser device is stored in the condensed water reservoir for a long period of time.

  Preferably, the internal combustion engine includes a turbine wheel that is rotated by energy of exhaust gas flowing through the exhaust passage, and a compressor impeller that is coupled to the turbine wheel and compresses air taken into the intake system. The exhaust gas introduced into the EGR cooler is taken out from the downstream side of the turbine wheel in the exhaust flow direction in the exhaust passage, and the intake system side connection is connected in the EGR passage. The part may be configured to be positioned upstream of the compressor impeller in the outside air suction direction in the intake system.

  In this configuration, when the application target of the present invention is an internal combustion engine with a turbocharger, it is possible to prevent moisture condensed by the condensing device from flowing into the intake system. Is less likely to be corroded or damaged by condensed water.

  Preferably, a collecting device may be provided between the condensing device and the condensate water reservoir to allow exhaust gas to pass therethrough and drop moisture condensed in the condensing device into the condensate water reservoir.

  In this configuration, the exhaust gas that has passed through the condensing device is allowed to pass, while the water condensed in the condensing device is dropped into the condensate pool, so that the condensate pools the condensate pool by the wind pressure of the exhaust gas. It becomes possible to prevent passing. As a result, the effect of preventing the inflow of condensed water into the intake system is enhanced.

  The exhaust gas recirculation apparatus for an internal combustion engine according to the present invention can condense water vapor mixed in the exhaust gas during operation of the internal combustion engine and prevent the condensed water from flowing into the intake system.

1 is a diagram showing a schematic configuration of an embodiment of an internal combustion engine to which the present invention is applied. It is a figure which shows the structure of the LPL-EGR apparatus of FIG. It is a graph which shows the condensed water generation | occurrence | production image relevant to the exhaust gas recirculation | reflux of the low pressure EGR path | route shown in FIG. It is a graph which shows the condensed water generation | occurrence | production image relevant to exhaust gas recirculation | reflux when a condensing apparatus, a collection apparatus, and a condensed water pool are excluded from the low voltage | pressure EGR channel | path shown in FIG.

  BEST MODE FOR CARRYING OUT THE INVENTION Best modes for carrying out the present invention will be described in detail below with reference to the accompanying drawings.

  1 to 3 show an embodiment of the present invention. In this embodiment, a case will be described in which the present invention is applied to a common rail in-cylinder direct injection multi-cylinder (for example, in-line 4-cylinder) diesel engine (hereinafter simply referred to as “engine”) mounted in an automobile.

  As shown in FIG. 1, the engine 1 is configured as a diesel engine system having a fuel supply system 2, a combustion chamber 3, an intake system 4, an exhaust system 5 and the like as main parts.

  The fuel supply system 2 is a “common rail system” including a common rail 21 common to all cylinders of the engine 1 and an injector (fuel injection valve) 22 of each cylinder.

  The common rail 21 is supplied with fuel pumped from a fuel tank (not shown) and pressurized by a supply pump (not shown). The common rail 21 has a function as a pressure accumulating chamber that holds (accumulates) high-pressure fuel at a predetermined pressure, and distributes the accumulated fuel to each injector 22 (in FIG. 1, only the right end is given a reference numeral).

  The injector 22 is attached to a cylinder head (not shown) and is configured to inject fuel directly into the combustion chamber 3, for example. The injector 22 is disposed substantially at the upper center of the combustion chamber 3 and injects fuel introduced from the common rail 21 toward the combustion chamber 3 at a predetermined timing. The injector 22 is a “piezo injector” that opens a piezoelectric element (piezo element) as appropriate and injects fuel into the combustion chamber 3.

  The supply pump supplies a part of the fuel pumped from the fuel tank to the fuel addition valve 23. The fuel addition valve 23 is constituted by an electronically controlled on-off valve, and is controlled by an electronic control unit (ECU) (not shown) when fuel is added to the exhaust system 5.

  The intake system 4 includes an intake manifold 41 connected to a plurality of intake ports (not shown) formed in a cylinder head (not shown). An intake pipe 42 is connected to the intake manifold 41. A portion where the intake manifold 41 and the intake pipe 42 are combined corresponds to an “intake passage”.

  In this intake passage, an air cleaner 43 and an intake throttle valve (electronically controlled throttle valve) 44 are arranged in order from the upstream side in the intake flow direction. An air flow meter 45 is installed downstream of the air cleaner 43 in the intake flow direction. The air flow meter 45 outputs an electrical signal corresponding to the amount of air flowing from the air cleaner 43 into the intake pipe 42.

  The exhaust system 5 includes an exhaust manifold 52 connected to an exhaust port 51 formed in the cylinder head. An exhaust pipe 53 is connected to the exhaust manifold 52. A portion where the exhaust manifold 52 and the exhaust pipe 53 are combined corresponds to an “exhaust passage”.

  The exhaust passage is provided with an oxidation catalyst 61, an NSR (NOx Storage Reduction) catalyst 62 that is an NOx storage reduction type exhaust purification catalyst, and a DPF (Diesel Particulate Filter) 63.

  The DPF 63 is made of, for example, a porous ceramic structure, and collects particulate matter (PM) contained in the exhaust gas when the exhaust gas passes through the porous wall. . A DPNR (Diesel Particulate-NOx Reduction system) catalyst may be used instead of the NSR catalyst 62 and the DPF 63.

  The engine 1 is provided with a turbocharger 7. The turbocharger 7 includes a turbine wheel 72 and a compressor impeller 73 that are connected by a turbine shaft 71.

  The compressor impeller 73 is arranged facing the inside of the intake pipe 42, and the turbine wheel 72 is arranged facing the inside of the exhaust pipe 53. The turbocharger 7 performs a supercharging operation of increasing the intake pressure by rotating the compressor impeller 73 using the exhaust flow (exhaust pressure) received by the turbine wheel 72.

  Further, an intake pipe 42 provided downstream of the compressor impeller 73 in the intake flow direction is provided with an intercooler 74 for forcibly cooling the intake air whose temperature has been raised by supercharging in the turbocharger 7. Yes.

  Further, the engine 1 is provided with an HPL-EGR device (high pressure EGR device) 8 and an LPL-EGR device (low pressure EGR device) 9.

  The HPL-EGR device 8 includes a high pressure EGR passage (high pressure exhaust gas recirculation passage) 81, a high pressure EGR valve 82, a high pressure EGR cooler 83, and the like.

  The high-pressure EGR passage 81 intakes the exhaust passage more upstream than the turbine wheel 72 of the turbocharger 7 in the exhaust flow direction (exhaust manifold 52) and the intake passage (intake pipe 42) than the intake throttle valve 44. A position downstream of the flow direction (position close to the intake manifold 41) is connected in communication.

  The high pressure EGR valve 82 changes the flow area of the high pressure EGR passage 81. The high pressure EGR cooler 83 cools the exhaust gas (high pressure EGR gas) flowing through the high pressure EGR passage 81.

  The amount of high pressure EGR gas recirculated (recirculated) by the HPL-EGR device 8 is adjusted by the opening degree of the high pressure EGR valve 82. When the air-fuel ratio is enriched using the HPL-EGR device 8, the amount of high-pressure EGR gas recirculated is increased and the amount of fresh air (the amount of oxygen in the intake system 4) is decreased. .

  The LPL-EGR device 9 includes a low pressure EGR passage (low pressure exhaust gas recirculation passage) 91, a low pressure EGR valve 92, a low pressure EGR cooler 93, and the like. In this embodiment, the LPL-EGR device 9 corresponds to the “exhaust gas recirculation device” according to the present invention.

  The low pressure EGR passage 91 is located at a position downstream of the NSR catalyst 62 (DPF 63 in this embodiment) in the exhaust flow direction in the exhaust passage (exhaust pipe 53) and upstream of the exhaust throttle valve 46 in the exhaust flow direction. And a position upstream of the compressor impeller 73 in the intake flow direction in the intake passage (intake pipe 42).

  The low pressure EGR valve 92 changes the flow area of the low pressure EGR passage 91. The low pressure EGR cooler 93 cools the exhaust gas (low pressure EGR gas) flowing through the low pressure EGR passage 91.

  The amount of low-pressure EGR gas recirculated (recirculated) by the LPL-EGR device 9 is adjusted by the opening degree of the low-pressure EGR valve 92. When the air-fuel ratio is enriched by using the LPL-EGR device 9, the recirculation amount of the low pressure EGR gas is increased and the amount of fresh air is decreased.

  By the way, the ECU refers to various maps stored in the ROM as needed based on the output from various sensors and the calculated value obtained by the calculation formula using the output value. Execute control. Examples of this control include, for example, fuel injection control (injection amount / injection timing control) by the injector 22, control of the opening of the intake throttle valve 44, opening of the high pressure EGR valve 82 and the low pressure EGR valve 92 (EGR gas amount). ) Control. Although not shown in the drawing, this ECU has a configuration including a microcomputer including a CPU, a ROM, a RAM, and the like and an input / output circuit as is well known.

  In this embodiment, the water vapor mixed in the exhaust gas purified by the purification unit (oxidation catalyst 61, NSR catalyst 62, DPF 63) is condensed, and the condensed water flows into the intake system 4 by separating it from the exhaust gas. It is devised not to let it.

  A configuration for realizing such separation of condensed water will be described.

  In the region from the low pressure EGR valve 92 to the connecting portion with the intake pipe 42 (intake system 4) in the low pressure EGR passage 91, the condensing device 11, the collecting device 12, and the condensed water reservoir 13 are in the exhaust flow direction in this order. It is provided in series from the upstream side.

  In the low pressure EGR passage 91, the region from the low pressure EGR valve 92 to the connecting portion with the intake pipe 42 (intake system 4) is obliquely downward on the most upstream side in the exhaust flow direction, as shown in FIG. It bends approximately 90 degrees from the obliquely downward portion 100 to become reversely obliquely downward, and makes a reverse turn upward from the inversely obliquely downward portion 200. A terminal portion of the reverse oblique upward portion 400 is connected to the intake pipe 42 (intake system 4).

  The condenser 11 condenses water vapor mixed in the exhaust gas introduced into the low-pressure EGR passage 91 and passed through the low-pressure EGR valve 92. Although not shown in detail, for example, the condenser 11 is dedicated to a heat exchange pipe. The cooling water cooled by the radiator is circulated. In short, the condensing device 11 condenses by cooling the water vapor mixed in the exhaust gas to its dew point temperature.

  The condensing device 11 is disposed on the upstream side in the exhaust flow direction of the reversely inclined downward portion 200 in the low-pressure EGR passage 91 described above. As a result, the condensing device 11 is installed in a posture such that it is disposed vertically below the low-pressure EGR valve 92 and the exhaust gas introduction side is positioned vertically above the discharge side. .

  The collection device 12 has a function of causing the exhaust gas to pass therethrough and causing moisture condensed in the condensation device 11 to collide and drop in the vertical direction, and is, for example, a mesh plate. The collection device 12 is disposed on the downstream side in the exhaust flow direction of the reversely inclined downward portion 200 in the low-pressure EGR passage 91 described above.

  The condensed water reservoir 13 stores water condensed by the condensing device 11. This condensate pool 13 is a U-turn portion 300 between the reverse obliquely downward portion 200 and the reverse obliquely upward portion 400 in the low-pressure EGR passage 91 described above. As a result, the condensate pool 13 is disposed at the lowest position in the vertical direction of the low-pressure EGR passage 91, so that it is disposed downstream of the condenser device 11 in the exhaust flow direction and below the condenser device 11 in the vertical direction. It has come to be.

  Further, the condensed water reservoir 13 is provided with a drain passage 14 for discharging the condensed water stored therein to the outside. It is conceivable that the condensed water discharged from the drain passage 14 is evaporated by being dropped onto the exhaust pipe 53, for example. In addition, although not shown in the drawings, an open / close valve may be provided in the drain passage 14 so that the open / close valve is opened when the amount of condensed water stored in the condensate pool 13 exceeds a predetermined value. It is.

  In this embodiment, a part of the relatively high temperature and high pressure exhaust gas discharged from the engine 1 to the exhaust manifold 52 is returned to the intake manifold 41 by the HPL-EGR device 8 during operation of the engine 1. . Further, a part of the relatively low temperature and low pressure exhaust gas purified by the purification unit (oxidation catalyst 61, NSR catalyst 62, DPF 63) through the turbine wheel 72 from the exhaust manifold 52 is taken in by the LPL-EGR device 9. The pipe 42 is recirculated to the upstream side in the intake flow direction of the compressor impeller 73 of the turbocharger 7.

  When the exhaust gas recirculated by the LPL-EGR device 9 passes through the low-pressure EGR cooler 93 and the low-pressure EGR valve 92 and flows into the condensing device 11, the exhaust gas passes through the condensing device 11 near the atmospheric temperature (specifically, Is cooled to the dew point temperature of water vapor mixed in the exhaust gas to be recirculated), so that water vapor mixed in the exhaust gas is condensed.

  This condensed water collides with the back wall of the collecting device 12 and the U-turn portion 300 by flowing in the reverse obliquely downward portion 200 of the low pressure EGR passage 91 with the wind pressure of the exhaust gas, and this collision causes Since the condensed water falls downward in the vertical direction in the u-turn portion 300, that is, the condensed water reservoir 13, it is stored in the condensed water reservoir 13.

  On the other hand, the exhaust gas that has passed through the collection device 12 is changed in direction by colliding with the back wall of the u-turn portion 300, passes through the reverse obliquely upward portion 400 obliquely upward, and flows into the intake system 4. become.

  By the way, the condensate pool 13 is disposed at the lowest position in the vertical direction in the low pressure EGR passage 91, and the most downstream region (reverse oblique upward portion 400) in the exhaust flow direction of the low pressure EGR passage 91 is obliquely upward. Therefore, although the wind pressure of the exhaust gas whose direction is changed acts on the condensed water stored in the condensed water reservoir 13, the condensed water is fed to the intake pipe 42 (intake system 4) by the wind pressure of the exhaust gas. It is never carried.

  For this reason, a part of the relatively low-temperature, low-pressure exhaust gas after passing through the purification unit (oxidation catalyst 61, NSR catalyst 62, DPF 63) by the LPL-EGR device 9 is used as the compressor impeller 73 of the turbocharger 7. The exhaust gas from which the water vapor has been removed can be recirculated to the intake pipe 42 (intake system 4) in the process of recirculation to the upstream side in the intake flow direction, and condensed water can be supplied to the recirculation destination (intake pipe 42). It can be prevented from entering.

  For reference, FIG. 3 illustrates an image in which condensed water is generated in connection with the exhaust gas recirculation in the low pressure EGR passage 91 in this embodiment. As a comparative example of this embodiment, an image in which condensed water is generated in relation to exhaust gas recirculation is illustrated in FIG. The comparative example has a configuration in which the condensing device 11, the collecting device 12, and the condensed water reservoir 13 are excluded from the low pressure EGR passage 91 of this embodiment.

  First, in the case of the comparative example, as shown in FIG. 4, since the temperature of the exhaust gas does not fall below the dew point temperature in the process in which the exhaust gas passes through the low pressure EGR passage 91, the water vapor mixed in the exhaust gas is reduced. It is hardly condensed. When this exhaust gas is mixed with the intake outside air (fresh air) by being recirculated to the upstream side in the intake flow direction of the compressor impeller 73 in the intake pipe 42, the exhaust gas is cooled and falls below the dew point temperature. The water vapor mixed in the exhaust gas begins to be condensed.

  Thereafter, as shown in FIG. 4, the temperature of the air-fuel mixture of the exhaust gas and the intake air rises due to the pressure change in the process of passing through the compressor impeller 73, so that the water vapor in the air-fuel mixture is not condensed. However, since the air-fuel mixture is cooled in the process of passing through the intercooler 74, the water vapor in the air-fuel mixture is condensed.

  On the other hand, in the case of this embodiment, as shown in FIG. 3, the exhaust gas is rapidly cooled in the process of passing through the condenser 11, the collector 12, and the condensed water reservoir 13 in the low pressure EGR passage 91. The temperature of the exhaust gas is lower than the dew point temperature, and the water vapor mixed in the exhaust gas is condensed at once. As described above, since the temperature of the exhaust gas is lowered and most of the water vapor mixed in the exhaust gas is condensed, the exhaust gas passes through the condensate pool 13 and is taken into the intake air of the compressor impeller 73 in the intake pipe 42. In the process of being mixed with the intake outside air by being refluxed upstream in the flow direction, the water vapor in the exhaust gas is condensed, but the amount of condensation is reduced.

  Thereafter, as shown in FIG. 3, as in the comparative example, the temperature of the air-fuel mixture of the exhaust gas and the intake air rises due to the pressure change in the process of passing through the compressor impeller 73, so that the water vapor in the air-fuel mixture is condensed. Not. Since the air-fuel mixture is cooled in the process of passing through the intercooler 74 and falls below the dew point temperature, the water vapor in the air-fuel mixture becomes condensed, but reaches the compressor impeller 73 as described above. Since much of the water vapor has been condensed and removed from the exhaust gas until this time, the amount of condensed water generated is reduced in the process in which the air-fuel mixture passes through the intercooler 74.

  Thus, in the case of this embodiment, the amount of condensed water generated in the process in which the exhaust gas passes through the low pressure EGR passage 91 is significantly larger than that in the comparative example of FIG. The amount is greatly reduced compared to the comparative example of FIG. This is advantageous in making it difficult for the condensed water to flow into the intake system 4.

  As described above, in the embodiment to which the present invention is applied, the exhaust gas purified by the purification unit (the oxidation catalyst 61, the NSR catalyst 62, the DPF 63) passes through the low pressure EGR passage 91 regardless of the operating state of the engine 1. In the process, the water vapor mixed in the exhaust gas is condensed and removed to make it difficult for the condensed water to flow into the intake system 4.

  As a result, metal parts (valves and the like) existing in the intake system 4 can be prevented from being corroded and damaged by the condensed water, and the condensed water can be prevented from entering the combustion chamber 3 of the engine 1. It becomes possible to avoid the water hammer phenomenon and misfire phenomenon with respect to the engine 1.

  Further, in this embodiment, the possibility that the low-pressure EGR cooler 93 is corroded and damaged by the condensed water is lower than that in the case where the water vapor mixed in the exhaust gas is condensed only by the low-pressure EGR cooler 93.

  Moreover, in this embodiment, since the drain passage 14 is provided in the condensed water reservoir 13, it is possible to avoid the occurrence of a problem that the condensed water reservoir 13 corrodes and opens a hole.

  Further, as in this embodiment, the application object of the present invention is the engine 1 with the turbocharger 7, and the exhaust gas is recirculated to the upstream side in the intake flow direction of the compressor impeller 73 by the LPL-EGR device 9. Even in such a case, the compressor impeller 73 is less likely to be corroded or damaged by condensed water.

  Furthermore, in this embodiment, since the collection device 12 is provided, it is possible to efficiently remove moisture condensed by the condensation device 11 from the exhaust gas by the collection device 12. As a result, the condensed water can be prevented from passing through the condensed water pool 13 due to the wind pressure of the exhaust gas, so that the effect of preventing the condensed water from flowing into the intake system 4 is improved.

  In addition, this invention is not limited only to the said embodiment, It can change suitably in the range equivalent to the claim and the said range.

  (1) In the above embodiment, the case where the HPL-EGR device 8 and the LPL-EGR device 9 are provided is described as an example, but the present invention is not limited to this. For example, the present invention can be applied to the case where any one of the HPL-EGR device 8 and the LPL-EGR device 9 is provided.

  (2) In the above embodiment, the engine 1 with the turbocharger 7 is given as an example of the application of the present invention. However, the present invention is not limited to this, and the turbocharger 7 is not limited thereto. It is possible to make the engine 1 to which this invention is not attached be an application object of this invention.

  (3) Although the example which made the collection apparatus 12 the mesh-shaped plate is given in the said embodiment, this invention is not limited only to this. Although not shown in the drawing, the collecting device 12 can be, for example, a centrifuge.

  The present invention can be suitably used in an exhaust gas recirculation device for recirculating exhaust gas discharged from an internal combustion engine to an exhaust passage to an intake system.

1 engine (internal combustion engine)
4 Intake System 5 Exhaust System 7 Turbocharger 72 Turbine Wheel 73 Compressor Impeller 8 HPL-EGR Device 9 LPL-EGR Device 91 Low Pressure EGR Passage 92 Low Pressure EGR Valve 93 Low Pressure EGR Cooler 11 Condensing Device 12 Collection Device 13 Condensate Pool 14 Drain passage

Claims (4)

An exhaust gas recirculation device for recirculating exhaust gas discharged from an internal combustion engine to an exhaust passage to an intake system,
An EGR passage that communicates and connects the exhaust passage and the intake system, an EGR cooler that cools exhaust gas introduced into the EGR passage, an EGR valve that opens and closes the outlet of the EGR cooler, and the EGR valve A condensing device for condensing water vapor contained in the passing exhaust gas, and a condensate pool for storing water condensed in the condensing device,
The condensing device is disposed in a vertical direction lower than the EGR valve, and is installed in such a posture that an exhaust gas introduction side is located on a vertical upper side than the discharge side,
The condensate pool is disposed on the downstream side in the exhaust flow direction from the condensing device and on the lower side in the vertical direction than the condensing device,
An exhaust gas recirculation apparatus for an internal combustion engine, characterized in that a region from the condensate pool to the intake system in the EGR passage is in a vertically upward direction from the condensate pool side to the intake system side. . The exhaust gas recirculation device for an internal combustion engine according to claim 1,
An exhaust gas recirculation apparatus for an internal combustion engine, wherein the condensed water reservoir is provided with a drain passage for discharging the water stored therein to the outside. The exhaust gas recirculation device for an internal combustion engine according to claim 1 or 2,
The internal combustion engine is provided with a turbocharger having a turbine wheel that is rotated by the energy of exhaust gas flowing in the exhaust passage and a compressor impeller that is connected to the turbine wheel and compresses air taken into the intake system. ,
Exhaust gas introduced into the EGR cooler is taken out from the downstream side of the turbine wheel in the exhaust flow direction in the exhaust passage,
The exhaust gas recirculation device for an internal combustion engine, wherein the connection portion on the intake system side in the EGR passage is positioned upstream of the compressor impeller in the intake air direction in the intake system. The exhaust gas recirculation device for an internal combustion engine according to any one of claims 1 to 3,
Between the condensing device and the condensed water reservoir, there is provided a collecting device for passing exhaust gas and dropping water condensed in the condensing device into the condensed water reservoir. Exhaust gas recirculation device.

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