JP5018400B2 - Exhaust gas recirculation device for internal combustion engine - Google Patents

Description

  The present invention relates to an exhaust gas recirculation device for an internal combustion engine that extracts exhaust gas from an exhaust passage of the internal combustion engine and guides the exhaust gas to an intake passage.

  As an exhaust gas recirculation device for an internal combustion engine, a part of the exhaust gas is taken out as an EGR gas from an exhaust passage downstream of a turbine of a turbocharger and introduced into an intake passage upstream of a compressor, and an exhaust gas is exhausted from an exhaust passage upstream of the turbine. A high-pressure exhaust gas recirculation passage that takes out a part as EGR gas and introduces it into an intake passage downstream of the compressor is known depending on the operating state of the internal combustion engine (Patent Document 1). In addition, Patent Documents 2 and 3 exist as prior art documents related to the present invention.

JP-A-2005-76456 Japanese Patent No. 2607175 JP 2003-269260 A

  When the low pressure exhaust gas recirculation passage is used, the EGR gas is guided upstream of the turbocharger compressor, so that carbon fine particles contained in the EGR gas and foreign matters such as water vapor, water droplets and freezing generated due to cooling of the EGR gas, etc. Flows into the compressor. The turbocharger compressor includes an impeller that rotates about an axis that passes through the center of the intake passage, and the impeller faces the intake passage. For this reason, foreign matter may collide with the impeller and promote damage or wear of the impeller.

  Therefore, an object of the present invention is to provide an exhaust gas recirculation device for an internal combustion engine that can suppress damage and wear of a compressor impeller due to collision of foreign matter contained in EGR gas.

Exhaust reflux device of the present invention, driving the compressor is provided to the compressor and an exhaust passage provided in the intake passage has an impeller which rotates about an axis extending so as to penetrate a central portion of the transverse intake passage And an exhaust gas recirculation passage which is applied to an internal combustion engine equipped with a turbocharger having a turbine to take out a part of exhaust gas as EGR gas from the exhaust passage and guides it into the intake passage upstream of the compressor. In the exhaust gas recirculation device for an internal combustion engine, the exhaust gas recirculation passage is disposed in the intake air passage and opens toward the downstream side of the intake air passage at the central portion of the intake air passage so that EGR gas is supplied to the intake air passage. introducing part can be guided is provided within said inlet portion, extends in the longitudinal direction of the intake passage, and suited to the downstream side of the intake passage An inner passage portion having a downstream opening portion that opens and an upstream opening portion that opens toward the upstream side of the intake passage, and a connection passage that is connected to the inner passage portion and guides EGR gas to the inner passage portion And the cross-sectional area of the connecting passage portion is set to be smaller than the opening area of the downstream opening portion of the inner passage portion, thereby solving the above-described problem (claims). 1).

  According to this exhaust gas recirculation device, the EGR gas is introduced into the intake passage from the introduction portion, whereby the EGR gas is guided to the rotation center portion of the impeller of the compressor. In other words, the introduction of EGR gas from the introduction portion causes the EGR gas concentration distribution in the central portion of the intake passage in the transverse direction to be higher than the concentration of EGR gas at the transverse end portion upstream of the compressor. It is formed. Therefore, even if the EGR gas contains foreign matters such as carbon fine particles, water vapor, water droplets, and icing, most of the foreign matters collide with the rotation center portion where the circumferential speed of the impeller is relatively low. Thereby, since the collision of the foreign material to the outer peripheral portion where the circumferential speed of the impeller is relatively high can be avoided, the impeller can be prevented from being damaged or worn by the collision of the foreign material contained in the EGR gas.

Further, according to the exhaust gas recirculation device of the present invention, the air guided to the intake passage can pass through the inner passage portion from the upstream opening toward the downstream opening, so the introduction portion is disposed in the intake passage. The increase in air resistance accompanying this can be suppressed. Further, according to the exhaust gas recirculation device of the present invention, the passage cross-sectional area of the connection passage portion is smaller than the opening area of the downstream opening portion of the inner passage portion, so the flow rate of the gas flowing out from the downstream opening portion and the inner passage portion The difference in flow rate from the flow rate of the gas flowing outside can be reduced. Thereby, mixing with the gas which flows out out of a downstream opening part, and the gas which flows the outer side of an inner side channel | path part can be suppressed. In other words, the diffusion of EGR gas is suppressed. Therefore, the EGR gas can be effectively concentrated on the rotation center portion of the impeller.

Various modes may be adopted as the inner passage portion. For example, the inner passage portion may be constituted by a tubular member disposed in a state surrounded by an inner wall of the intake passage ( Claim 2 ), and the inner passage portion may be formed in a transverse direction of the intake passage and A pair of partition walls extending in the longitudinal direction and connected to the inner wall of the intake passage, and an inner wall of the intake passage sandwiched between the pair of partition walls ( claim 3 ). . In particular, in the former case, the EGR gas guided to the inner passage portion is prevented from spreading in the transverse direction of the intake passage, so that the EGR gas can be effectively concentrated on the rotation center portion of the impeller.

  As described above, according to the present invention, the EGR gas is introduced into the intake passage from the introduction portion, whereby the EGR gas is guided to the rotation center portion of the compressor impeller. For this reason, even if the EGR gas contains foreign matters such as carbon fine particles, water vapor, water droplets, and icing, most of the foreign matters collide with the center of rotation of the impeller where the circumferential speed is relatively low. It is possible to avoid collision of a foreign object with the outer peripheral portion having a relatively high value. Thereby, the damage and wear of the impeller due to the collision of the foreign matter contained in the EGR gas can be suppressed.

(First form)
FIG. 1 shows an internal combustion engine in which an exhaust gas recirculation apparatus according to an embodiment of the present invention is incorporated. The internal combustion engine 1 is mounted on a vehicle as a driving power source, and is configured as an in-line four-cylinder type diesel engine in which four cylinders 2 are arranged in one direction. Each cylinder 2 is provided with a fuel injection valve 3 so that its tip faces the cylinder 2, and these fuel injection valves 3 are connected to a common rail 4 that holds the fuel at a predetermined fuel pressure. Yes. An intake passage 6 and an exhaust passage 7 are connected to each cylinder 2. The intake passage 6 includes an intake manifold 8 branched for each cylinder 2, and the exhaust passage 7 includes an exhaust manifold 9 that collects exhaust discharged from each cylinder 2. The internal combustion engine 1 fills each cylinder 2 with air filtered through the intake duct 10 via the intake manifold 8 and self-ignites the fuel injected into each cylinder 2 by the fuel injection valve 3 in the compression stroke. Let Exhaust gas discharged from each cylinder 2 is collected by an exhaust manifold 9, and the collected exhaust gas is discharged into the atmosphere after harmful substances are purified by an exhaust gas purification device 11.

  The internal combustion engine 1 is equipped with a turbocharger 12 that supercharges air using exhaust energy. The turbocharger 12 includes a compressor 13 provided in the intake passage 6 and a turbine 14 provided in the exhaust passage 7, and is a known one that drives the compressor 13 by the turbine 14 that has obtained exhaust energy. The compressor 13 includes an impeller 15, and the impeller 15 is accommodated in a compressor housing 16. The turbine 14 includes a turbine blade 17, and the turbine blade 17 is accommodated in a turbine housing 18. These housings 16 and 18 are connected to a center housing 19, and a bearing 19 a that rotatably supports a rotating shaft 20 that connects the impeller 15 and the turbine blade 17 so as to rotate together is mounted on the center housing 19. ing. The rotary shaft 20 is supported so as to be rotatable about an axis Ax1 extending so as to penetrate the central portion 6a in the transverse direction of the intake passage 6. Therefore, the impeller 15 and the turbine blade 17 can rotate about the axis Ax1, respectively. The compressor housing 16 is part of the intake passage 6 and includes an opening 16a that opens in the direction of the axis Ax1. The turbine housing 18 forms a part of the exhaust passage 7 and includes an opening 18a.

  An intake air cooling intercooler 21 is provided in the intake passage 6 on the downstream side of the compressor 13. Further, the exhaust passage 7 is provided with a supercharging pressure adjusting device 22 that adjusts the supercharging pressure within an allowable limit. The supercharging pressure adjusting device 22 bypasses the turbine 14 and sends exhaust gas downstream of the turbine 14. A bypass passage 23 for guiding and a waste gate valve 24 for opening and closing the bypass passage 23 are provided.

  The internal combustion engine 1 is provided with an exhaust gas recirculation device 25 that suppresses an increase in the combustion temperature in the cylinder 2 by recirculating exhaust gas to the intake system. The exhaust gas recirculation device 25 takes out part of the exhaust gas from the exhaust passage 7 as EGR gas and introduces it into the intake air passage 6 upstream of the compressor 13, a cooling device 27 that cools the EGR gas, and the exhaust gas recirculation passage. And an exhaust gas recirculation valve 28 for adjusting the flow rate of the EGR gas flowing through the exhaust gas 26. The amount of EGR gas introduced into the intake passage 6 (EGR amount) is set according to the operating state of the internal combustion engine 1, and the EGR amount is adjusted from the opening of the exhaust gas recirculation valve 28 and the EGR gas introduction position. This is also implemented by operating the throttle valve 29 provided in the upstream intake passage 6 in association with the opening.

  The exhaust gas recirculation passage 26 is provided with an introduction portion 30 disposed in the intake passage 6. 2 is an enlarged view of the introduction portion 30 and its periphery, and FIG. 3 is a schematic cross-sectional view taken along the line III-III of FIG. As shown in these drawings, the introduction portion 30 includes a tubular member 31 extending in the longitudinal direction of the intake passage 6 and a connection passage portion 32 connected to the tubular member 31. The tubular member 31 is disposed in the central portion 6a in a state surrounded by the inner wall 6b of the intake passage 6 and opens toward the upstream side and the downstream opening portion 31a that opens toward the downstream side of the intake passage 6. And an upstream opening 31b. The opening areas of these openings 31a and 31b are set to the same area. The tubular member 31 constitutes an inner passage portion according to the present invention. The connection passage portion 32 is opened on the inner peripheral surface of the tubular member 31, whereby the connection passage portion 32 can guide the EGR gas to the tubular member 31 as indicated by a broken arrow in FIG.

  As is apparent from FIGS. 2 and 3, the EGR gas is introduced into the intake passage 6 from the tubular member 31, whereby the EGR gas is guided to the rotation center portion of the impeller 15 of the compressor 13. That is, due to the introduction of EGR gas from the tubular member 31, the EGR gas concentration distribution in which the concentration of EGR gas at the center in the transverse direction of the intake passage 6 is higher than the concentration of EGR gas at the end in the transverse direction is Formed upstream. Therefore, even if the EGR gas contains foreign matters such as carbon fine particles, water vapor, water droplets and freezing, the foreign matters collide with the rotation center portion of the impeller 15 having a relatively low circumferential speed. Thereby, since the collision of the foreign material to the outer peripheral portion having a relatively high circumferential speed is avoided, damage and wear of the impeller 15 due to the collision of the foreign material can be suppressed. The distance between the downstream opening 31a and the impeller 15 is set within a range in which the above-described concentration distribution is maintained. This is because if the distance is excessive, the intended effect is reduced because the EGR gas diffuses.

  Since the tubular member 31 also has the upstream opening 31b, air flows into the tubular member 31 and flows out from the downstream opening 31a together with the EGR gas. That is, since air guided to the intake passage 6 can pass through the tubular member 31, an increase in air resistance due to the arrangement of the tubular member 31 can be suppressed.

  The passage cross-sectional area of the connection passage portion 32 is set to be smaller than the opening area of the downstream side opening portion 31 a of the tubular member 31. Therefore, the flow rate difference between the flow rate of the gas flowing out from the downstream opening 31a and the flow rate of the gas flowing outside the tubular member 31 can be suppressed. Thereby, mixing with the gas which flows out out of the downstream opening part 31a, and the gas which flows the outer side of the tubular member 31 can be suppressed. Further, since the EGR gas passes through the tubular member 31, it is possible to suppress the EGR gas from spreading in the transverse direction of the intake passage 6. Thereby, EGR gas can be effectively concentrated on the rotation center part of the impeller 15.

(Second form)
Next, a second embodiment of the present invention will be described with reference to FIGS. This form has the same structure as the first form except for the structure of the introduction part. Hereinafter, the characteristic part of the second embodiment will be described, and the description of the common part with the first embodiment will be omitted.

  4 is an enlarged view of the introduction portion 40 and its periphery according to the second embodiment, and FIG. 5 is a schematic cross-sectional view taken along the line V-V in FIG. As shown in these drawings, the introduction portion 40 according to the second embodiment is disposed in the central portion 6a of the intake passage 6 and extends in the longitudinal direction thereof, and a connection connected to the inner passage portion 41. And a passage portion 42. The inner passage portion 41 extends in the transverse direction and the longitudinal direction of the intake passage 6 and is connected to the inner wall 6 b of the intake passage 6, and the intake passage sandwiched between the partition wall portions 43. 6 inner walls 6b. The pair of partition wall portions 43 are arranged in parallel with each other at a predetermined interval. The inner passage 41 has a downstream opening 41a that opens toward the downstream side of the intake passage 6 and an upstream opening 41b that opens toward the upstream side thereof. The opening areas of these openings 41a and 41b are set to the same area. The connection passage portion 42 opens to the inner side of the inner passage portion 41, so that the connection passage portion 42 can guide EGR gas to the inner passage portion 41 as indicated by the dashed arrow in FIG. 4. The passage cross-sectional area of the connection passage portion 41 is set to be smaller than the opening area of the downstream side opening portion 41 a of the inner passage portion 41. According to this embodiment, the EGR gas is introduced into the intake passage 6 from the inner passage portion 41, whereby the EGR gas is guided to the rotation center portion of the impeller 15 of the compressor 13. Thereby, an effect substantially equivalent to the effect of the 1st form mentioned above is exhibited.

( First reference example )
Next, a first reference example having parts common to the embodiment of the present invention will be described with reference to FIGS. This reference example has the same configuration as the first embodiment except for the configuration of the introduction part. Hereinafter, the characteristic part of the first reference example will be described, and the description of the common part with the first embodiment will be omitted.

FIG. 6 is an enlarged view of the introduction portion 50 and its periphery according to the first reference example , and FIG. 7 is a schematic cross-sectional view taken along the line VII-VII of FIG. As shown in these drawings, the introduction portion 50 according to the first reference example is disposed in the central portion 6a of the intake passage 6 and extends in the longitudinal direction thereof, and also opens downstream toward the downstream side of the intake passage 6. An opening 50a is provided. Although not shown, the introduction portion 50 may be bent to the outside in the transverse direction on the upstream side of the intake passage 6 and connected to the exhaust gas recirculation passage 26. Further, when the intake passage 6 is bent at the upstream side thereof, the introduction portion 50 may extend straight and be connected to the exhaust gas recirculation passage 26 at the bent portion of the intake passage 6.

According to the first reference example , the EGR gas is introduced into the intake passage 6 from the inner passage portion 41, whereby the EGR gas is guided to the rotation center portion of the impeller 15 of the compressor 13. Thereby, breakage and wear of the impeller 15 due to the collision of the foreign matter contained in the EGR gas can be suppressed.

( Second reference example )
Next, a second reference example having portions common to the embodiment of the present invention will be described with reference to FIGS. This reference example corresponds to a modification of the first reference example . Therefore, the description of the common part with the first reference example is omitted. FIG. 8 is an enlarged view of the introduction portion 50 and its periphery according to the second reference example , and FIG. 9 is a schematic cross-sectional view taken along the line IX-IX in FIG. As shown in these drawings, the second reference example includes a surrounding passage portion 51 surrounding the introduction portion 50. The surrounding passage portion 51 is disposed in the intake passage 6 and opens toward the upstream side and the downstream side of the intake passage 6. The downstream opening 51 a is located on the downstream side of the opening 50 a of the introduction part 50. As shown in FIG. 9, the surrounding passage portion 51 is disposed substantially coaxially with the introduction portion 50 and is configured in a cylindrical shape.

According to the second reference example, it is possible to achieve the first reference example and the same effect is prevented from EGR gas flowing out from the inlet section 50 extends in the transverse direction of the intake passage 6 by surrounding the passage portion 51 Therefore, the EGR gas can be effectively concentrated on the center of rotation of the impeller 15.

( Third reference example )
Next, a third reference example having portions common to the embodiment of the present invention will be described with reference to FIGS. Note that, in the following description, the same reference numerals are given to the configurations common to the above-described embodiments of the present invention or the respective reference examples, and the description is omitted. The third reference example is characterized in that air containing no EGR gas is introduced from the outer peripheral side of the intake passage in order to form the above-described EGR gas concentration distribution upstream of the compressor. FIG. 10 shows an internal combustion engine in which an exhaust gas recirculation apparatus according to a third reference example is incorporated. The internal combustion engine 1 of FIG. 10 is provided with an air passage 61 for introducing air into the intake passage 6 downstream of the junction 60 between the exhaust recirculation passage 26 and the intake passage 6 and upstream of the compressor 13. . One end of the air passage 61 is connected upstream of the throttle valve 29, and an air introduction portion 62 is provided at the other end.

  FIG. 11 is an enlarged view of the air introduction part 62 and its periphery, and FIG. 12 is a schematic cross-sectional view taken along line XII-XII in FIG. As shown in these drawings, the air introduction portion 62 opens from the outer peripheral side of the intake passage 6 to the inner peripheral side and guides air into the intake passage 6, so that the air introduction portion 62 moves from the outer peripheral side of the intake passage 6 toward the inner peripheral side. And four air introduction ports 63 that penetrate therethrough and an air introduction chamber 64 that surrounds the outer peripheral surface of the intake passage 6 so as to cover the introduction port 63 and communicates with the air passage 62.

As shown in FIG. 10, the internal combustion engine 1 can limit the flow rate of air flowing into the intake passage 6 separately from the air introduced through the air passage 61 by restricting the intake passage 6 with the throttle valve 29. By restricting the flow rate of the air, the flow rate of the air introduced in the air passage 61 is relatively increased . Operation of throttles valve 29 can be optionally set, but it is possible to operate the throttle valve 29 so that the opening for example as a gas amount of the EGR gas increases throttled.

According to the third reference example , air that does not contain EGR gas is introduced into the intake passage 6 by the air passage 61, so that it is radially outside in the intake passage 6, that is, at the end in the transverse direction of the intake passage 6. Air can be unevenly distributed. As a result, the EGR gas guided to the intake passage 6 via the junction 50 is guided to the central portion 6 a of the intake passage 6. Therefore, an EGR gas concentration distribution in which the concentration of EGR gas in the central portion 6 a in the transverse direction of the intake passage 6 is higher than the concentration of EGR gas in the end portion in the transverse direction can be formed upstream of the compressor 13.

( Fourth reference example )
Next, a fourth reference example having parts common to the embodiment of the present invention will be described with reference to FIGS. This reference example corresponds to a modification of the third reference example . Therefore, the description of the common part with the third reference example is omitted.

FIG. 13 is an enlarged view of the air introduction part and its periphery according to the fourth reference example , and FIG. 14 is a schematic sectional view taken along the line XIV-XIV in FIG. As shown in these drawings, the air passage 71 of this reference example has an air introduction portion 72. Although not shown, one end of the air passage 71 is connected to the upstream side of the throttle valve 29 as in the third reference example . Similarly to the third reference example , the air introduction part 72 includes four air introduction ports 73 that penetrate from the outer peripheral side to the inner peripheral side of the intake passage 6 and the intake passage 6 so as to cover the introduction port 73. And an air introduction chamber 74 that communicates with the air passage 61. Further, the air introduction portion 72 further includes a flap 75 as a swirl flow generating means for imparting a swirl flow F swirling in the circumferential direction of the intake passage 6 to the air guided into the intake passage 6. In this reference example , a total of four flaps 75 are provided for each air inlet 73. Each flap 75 is configured to extend in the substantially same direction as the tangential direction of the inner peripheral surface of the intake passage 6. As a result, the flow direction of the air from the air introduction chamber 74 to the intake passage 6 via the air introduction port 73 is aligned with the tangential direction by the flap 75, so that the swirl flow F swirling in the circumferential direction of the intake passage 6 It is formed in the intake passage 6.

According to the fourth reference example , in addition to being able to exhibit the same effect as the third reference example , the swirling flow F is given to the air guided into the intake passage 6, so that the swirling flow is given. It becomes easy to make air unevenly distributed to the end of the intake passage 6 in the transverse direction. In other words, the centrifugal force of the swirling flow F makes it difficult for the air to diffuse toward the central portion 6a of the intake passage 6 and to stay at the end.

In the third and fourth reference examples , the exhaust gas recirculation passage 26 may be provided with the introduction parts 30 and 40 according to each aspect of the present invention described above and the introduction part 50 of the first or second reference example. 11 and 13, the exhaust gas recirculation passage 26 may simply be connected to the intake passage 6. When the introduction portions 30 and 40 of the above-described embodiments of the present invention and the introduction portion 50 of the first or second reference example are provided in the exhaust gas recirculation passage 26, EGR gas is introduced into the intake passage at these introduction portions. Since the air can be unevenly distributed to the end portion in a state of being concentrated on the central portion 6a of the air intake 6, the concentration of the concentration distribution of the EGR gas in the intake passage 6 can be made more conspicuous .

In the third and fourth reference examples , one end of the air passage is connected to the intake passage to extract air, but by connecting one end of the air passage to an air supply source that is different from the intake passage. Limited may be subjected. In this case, air can be pumped to the outer periphery of the intake passage using pressurizing means such as an air pump.

The figure which showed the internal combustion engine in which the exhaust gas recirculation apparatus which concerns on one form of this invention was integrated. The enlarged view to which the introduction part shown by FIG. 1 and its periphery were expanded. The cross-sectional schematic diagram along the III-III line of FIG. The enlarged view which expanded the introduction part and its periphery which concern on a 2nd form. The cross-sectional schematic diagram along the VV line | wire of FIG. The enlarged view which expanded the introduction part and its periphery which concern on the 1st reference example with respect to embodiment of this invention . FIG. 7 is a schematic sectional view taken along line VII-VII in FIG. 6. The enlarged view which expanded the introduction part and its periphery which concern on the 2nd reference example with respect to embodiment of this invention . FIG. 9 is a schematic cross-sectional view taken along line IX-IX in FIG. 8. The figure which showed the internal combustion engine in which the exhaust gas recirculation apparatus which concerns on the 3rd reference example with respect to embodiment of this invention was integrated. The enlarged view to which the air introduction part of FIG. 10 and its periphery were expanded. FIG. 12 is a schematic sectional view taken along line XII-XII in FIG. 11. The enlarged view which expanded the air introduction part which concerns on the 4th reference example with respect to embodiment of this invention, and its periphery. FIG. 14 is a schematic sectional view taken along line XIV-XIV in FIG. 13.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Internal combustion engine 6 Intake passage 6a Center part 6b Inner wall 7 Exhaust passage 12 Turbocharger 13 Compressor 14 Turbine 15 Impeller 26 Exhaust recirculation passage 29 Throttle valve (flow restriction means)
30 Introduction part (concentration distribution forming means)
31 Tubular member (inner passage)
31a Downstream side opening 31b Upstream side opening 32 Connection passage part 40 Introduction part 41 Inner passage part 41a Downstream side opening part 41b Upstream side opening part 42 Connection passage part 43 Partition wall part 50 Introduction part 50a Downstream side opening part 51 Surrounding passage Part 60 confluence part 61 air passage (concentration distribution forming means)
62 Air introduction part 71 Air passage (concentration distribution forming means)
Ax1 Axis F Swirling flow

Claims (3)

A turbocharger having an impeller that rotates about an axis extending so as to pass through a central portion in a transverse direction of the intake passage, and a compressor that is provided in the intake passage and a turbine that is provided in the exhaust passage and drives the compressor In an exhaust gas recirculation apparatus for an internal combustion engine, which is applied to an internal combustion engine mounted, and includes an exhaust gas recirculation passage that takes out a part of exhaust gas as EGR gas from the exhaust passage and guides the exhaust gas into the intake passage upstream of the compressor.
The exhaust gas recirculation passage is disposed in the intake passage and opens toward the downstream side of the intake passage at the central portion of the intake passage so that EGR gas can be introduced into the intake passage. Is provided ,
The introduction portion extends in the longitudinal direction of the intake passage and has an inner side having a downstream opening that opens toward the downstream side of the intake passage and an upstream opening that opens toward the upstream side of the intake passage. A passage portion, and a connection passage portion that is connected to the inner passage portion and guides EGR gas to the inner passage portion,
An exhaust gas recirculation device for an internal combustion engine, characterized in that a passage sectional area of the connection passage portion is set to be smaller than an opening area of the downstream opening portion of the inner passage portion . 2. The exhaust gas recirculation device for an internal combustion engine according to claim 1 , wherein the inner passage portion is constituted by a tubular member disposed in a state surrounded by an inner wall of the intake passage. The inner passage portion includes a pair of partition walls extending in a transverse direction and a longitudinal direction of the intake passage and connected to the inner wall of the intake passage, and the intake passage sandwiched between the pair of partition walls. The exhaust gas recirculation device for an internal combustion engine according to claim 1 , wherein the exhaust gas recirculation device is constituted by an inner wall.

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