JP2006037773A - Exhaust gas recirculation control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an exhaust gas recirculation control device which appropriately controls temperature of exhaust gas led to an exhaust system of an engine. <P>SOLUTION: The device is provided with a cooling passage 75 for circulating exhaust gas being cooled, a bypass passage 81 for circulating exhaust gas by bypassing the cooling passage 75, a partition wall 58 for partitioning an outlet 72 of the cooling passage 75 and an outlet 73 of the bypass passage 81, a swing valve 56 for opening/closing respective outlets 72, 73 of the cooling passage 75 and the bypass passage 81, a lead-out port 83 for leading out exhaust gas to an intake system of an engine by communicating to one of the cooling passage 75 and the bypass passage 81 in which one of the outlets 72, 73 is opened. The partition wall 58 is offset to the bypass passage 81 side with respect to the center axial line O of the lead-out port 83. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an exhaust gas recirculation control device (hereinafter referred to as “exhaust gas recirculation”) that controls the temperature of exhaust gas to be recirculated by introducing it into the intake system of an internal combustion engine (hereinafter referred to as “the internal combustion engine”). About).

  Patent Document 1 discloses an EGR control device that includes a cooling passage that circulates exhaust gas while cooling, a bypass passage that circulates the exhaust gas around the cooling passage, and a swing valve that opens and closes the passage. Has been. In this EGR control device, by opening the cooling passage and closing the bypass passage, the low-temperature exhaust gas that has passed through the cooling passage can be guided to the intake system, and on the other hand, by closing the cooling passage and opening the bypass passage, The hot exhaust gas that has passed through the passage can be guided to the intake system.

International Publication No. 03/062625 Pamphlet

In the EGR control device disclosed in Patent Document 1, if both the cooling passage and the bypass passage are opened, it is possible to guide the exhaust gas at an intermediate temperature to the intake system. However, in the EGR control device of Patent Document 1 in which the inlet portion of each passage is opened and closed by a swing valve, even if exhaust gas flows out from the outlet portion of each passage and merges, it is difficult to mix. For this reason, the temperature of the exhaust gas guided to the intake system after such merging cannot be properly controlled. For example, when feedback control is performed on the exhaust gas temperature leading to the intake system, it becomes difficult to accurately detect the exhaust gas temperature after merging, and the exhaust gas temperature actually guided to the intake system deviates from the optimum temperature. End up. When exhaust gas having the optimum temperature cannot be led to the intake system as described above, problems such as engine emission failure and drivability deterioration in a vehicle equipped with an EGR control device occur.
An object of the present invention is to provide an EGR control device that appropriately controls the temperature of exhaust gas led to an intake system of an engine.

  According to the first aspect of the present invention, the partition partitioning the outlet portion of the cooling passage opened and closed by the swing valve and the outlet portion of the bypass passage is offset to the cooling passage side or the bypass passage side with respect to the central axis of the outlet port. is doing. Therefore, when the outlet portions of both the cooling passage and the bypass passage are opened by the swing valve, the exhaust gas from each passage joins asymmetrically with respect to the central axis of the outlet port at the outlet ports communicating with the outlet portions. It becomes a flow. Due to the occurrence of this turbulent flow, the exhaust gas from each passage easily mixes with the merging at the outlet. Moreover, in the first aspect of the present invention, by swinging the swing valve between the first swing position for closing the outlet portion of the cooling passage and the second swing position for closing the outlet portion of the bypass passage, The mixing ratio of the exhaust gas from the passage can be freely changed. As described above, according to the first aspect of the present invention, it is possible to appropriately control the temperature of the exhaust gas that joins at the outlet and is led to the intake system of the engine.

  According to the second aspect of the present invention, the outlet portion of the cooling passage opened and closed by the swing valve and the outlet portion of the bypass are partitioned by the partition wall, and the swing shaft of the swing valve extending in the width direction of both passages is provided. It is offset to the cooling passage side or the bypass passage side with respect to the center axis of the outlet. Therefore, when the outlet portions of both the cooling passage and the bypass passage are opened by the oscillating valve, the exhaust gas from each passage is along the oscillating valve with respect to the central axis of the outlet port at the outlet ports communicating with the outlet portions. It merges asymmetrically and becomes turbulent. Due to the occurrence of this turbulent flow, the exhaust gas from each passage easily mixes with the merging at the outlet. In addition, in the invention described in claim 2, by swinging the swing valve between the first swing position for closing the outlet portion of the cooling passage and the second swing position for closing the outlet portion of the bypass passage, The mixing ratio of the exhaust gas from the passage can be freely changed. As described above, according to the second aspect of the present invention, it is possible to appropriately control the temperature of the exhaust gas that joins at the outlet and is led to the intake system of the engine.

  According to the third and fourth aspects of the present invention, the swing valve that opens and closes each outlet of the cooling passage and the bypass partitioned by the partition has a valve body and a protrusion. Here, the protrusion protrudes from the plate-shaped valve body to at least one side of the first swing position for closing the outlet portion of the cooling passage and the second swing position for closing the outlet portion of the bypass passage. Therefore, when the outlet of both the cooling passage and the bypass passage is opened by the swing valve, and the exhaust gas from each passage flows into the outlet port communicating with the outlet, the exhaust that has collided with the protrusion of the swing valve The gas flow becomes turbulent. Due to the occurrence of this turbulent flow, the exhaust gas from each passage easily mixes with the merging at the outlet. In addition, according to the third and fourth aspects of the present invention, the mixing ratio of the exhaust gas from each passage is freely changed by swinging the swing valve between the first swing position and the second swing position. Can be made. As described above, according to the third and fourth aspects of the present invention, it is possible to appropriately control the temperature of the exhaust gas that merges at the outlet and is led to the intake system of the engine.

  According to the fifth aspect of the present invention, the outlet portion of the cooling passage opened and closed by the swing valve and the outlet portion of the bypass are partitioned by the partition walls, and the outlet portions are respectively sandwiched between the outlet portions on the opposite side of the partition walls. The provided first inclined wall and second inclined wall are inclined with respect to the central axis of the outlet. Here, the inclination angles of the first and second inclined walls with respect to the central axis of the outlet are different. Therefore, when the outlet portions of both the cooling passage and the bypass passage are opened by the swing valve, the exhaust gases from the cooling passage and the bypass passage are respectively connected to the first inclined wall and the second outlet at the outlet port communicating with the outlet portions. Along the inclined wall, it merges asymmetrically with respect to the central axis of the outlet, resulting in turbulent flow. Due to the occurrence of this turbulent flow, the exhaust gas from each passage easily mixes with the merging at the outlet. In addition, in the invention described in claim 5, each of the swing valves is swung between a first swing position for closing the outlet portion of the cooling passage and a second swing position for closing the outlet portion of the bypass passage. The mixing ratio of the exhaust gas from the passage can be freely changed. As described above, according to the fifth aspect of the present invention, it is possible to appropriately control the temperature of the exhaust gas that joins at the outlet and is led to the intake system of the engine.

  According to the invention described in claim 6, the outlet portion of the cooling passage opened and closed by the swing valve and the outlet portion of the bypass are partitioned by the partition wall, and at least one offset portion of the cooling passage and the bypass passage is the center of the outlet The cooling passage and the bypass passage are offset in the width direction with respect to the axis. Therefore, when the outlet portions of both the cooling passage and the bypass passage are opened by the swing valve, the exhaust gas from each passage joins asymmetrically with respect to the central axis of the outlet port at the outlet ports communicating with the outlet portions. It becomes a flow. Due to the occurrence of this turbulent flow, the exhaust gas from each passage easily mixes with the merging at the outlet. In addition, in the invention described in claim 6, by swinging the swing valve between the first swing position for closing the outlet portion of the cooling passage and the second swing position for closing the outlet portion of the bypass passage, The mixing ratio of the exhaust gas from the passage can be freely changed. As described above, according to the sixth aspect of the present invention, it is possible to appropriately control the temperature of the exhaust gas that joins at the outlet and is led to the intake system of the engine.

  According to the invention described in claim 7, the flow blocking member provided in at least one of the outlet portion of the cooling passage and the outlet portion of the bypass passage blocks the flow of the exhaust gas. Therefore, in the passage where the current blocking member is provided in the outlet portion, the flow of the exhaust gas collides with the current blocking member and becomes a turbulent flow. Occurrence of this turbulent flow makes it easier for the exhaust gas from each passage to be mixed at the outlet port when the outlet portions of both the cooling passage and the bypass passage are opened.

  According to the eighth aspect of the present invention, the flow blocking member provided in the outlet port blocks the flow of the exhaust gas. Therefore, when the outlet portions of both the cooling passage and the bypass passage are opened, the exhaust gas flows from each passage into the turbulent flow by colliding with the current shielding member at the outlet, so that the exhaust gas is more easily mixed. Become.

  Of the invention according to claim 1, the invention according to claim 2, the invention according to claim 3 or 4, the invention according to claim 5, and the invention according to claim 6. You may make it combine at least two. Further, the combined invention and the invention described in claim 7 or 8 may be further combined.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
FIG. 2 shows an engine system 10 according to a first embodiment to which the present invention is applied. An engine system 10 mounted and used in a vehicle includes an engine 12, an intake system 20, an exhaust system 30, an EGR system 40, and the like.

  The intake system 20 includes an intake pipe 21, an intake manifold 22, an air cleaner 23, and a throttle device 24. The intake pipe 21 and the intake manifold 22 form an intake passage through which air sucked from outside the vehicle flows. In the middle of the intake pipe 21, an air cleaner 23 and a throttle device 24 are interposed in this order from the upstream side. The air cleaner 23 removes foreign matter in the intake air flowing through the intake passage. The throttle device 24 adjusts the flow rate of intake air in the intake passage. The intake manifold 22 that connects the intake pipe 21 and the engine 12 includes a surge tank 26 and a plurality of branch pipes 27. The intake air whose flow rate is adjusted by the throttle device 24 is pulsated by the surge tank 26 and then distributed to each cylinder of the engine 12 by each branch pipe 27.

  The exhaust system 30 has an exhaust manifold 31 and an exhaust pipe 32. The exhaust manifold 31 and the exhaust pipe 32 form an exhaust passage through which exhaust gas discharged from the engine 12 flows. The exhaust manifold 31 includes a plurality of branch pipes 34 and a merging portion 35. Exhaust gases discharged from the cylinders of the engine 12 to the branch pipes 34 merge at the merge portion 35. The exhaust pipe 32 is connected to the junction 35 and discharges exhaust gas flowing from the junction 35 to the outside of the vehicle through the muffler of the vehicle.

  The EGR system 40 includes a reflux pipe 41, a temperature adjustment device 42, a flow rate adjustment device 43, a temperature sensor 44, and a controller 45. The recirculation pipe 41 is connected between the merging portion 35 of the exhaust manifold 31 and the surge tank 26 of the intake manifold 22, and a part of the exhaust gas flowing from the merging portion 35 is led to the surge tank 26 and recirculated to the engine 12. An EGR passage to be circulated is formed. A temperature adjusting device 42 and a flow rate adjusting device 43 are interposed in this order from the upstream side in the middle of the reflux pipe 41. That is, the reflux pipe 41 includes a first pipe part 47 between the merging part 35 and the temperature adjustment apparatus 42, a second pipe part 48 between the temperature adjustment apparatus 42 and the flow rate adjustment apparatus 43, and a flow rate adjustment apparatus 43 and a surge. A third pipe portion 49 between the tank 26 and the tank 26 is provided. The temperature adjusting device 42 is electrically connected to the controller 45, and adjusts the temperature of the exhaust gas led to the surge tank 26 in accordance with a command from the controller 45. The flow rate adjusting device 43 is electrically connected to the controller 45, and adjusts the flow rate of the exhaust gas led to the surge tank 26 by changing the opening of the EGR valve in accordance with a command from the controller 45. The temperature sensor 44 is attached to the third pipe portion 49 and detects the temperature of the exhaust gas led to the surge tank 26. The temperature sensor 44 is electrically connected to the controller 45, and outputs the detection result of the exhaust gas temperature to the controller 45. The controller 45 is mainly composed of a microcomputer and controls the temperature adjusting device 42, the flow rate adjusting device 43, and the like.

Next, the temperature adjustment device 42 and the controller 45 will be described in detail. As shown in FIGS. 3 and 4, the temperature adjustment device 42 includes an introduction part 51, a cooling part 52, a bypass part 53, a partition wall 58, a valve support part 54, a lead-out part 55, a swing valve 56, and a valve drive part 57. ing.
The introduction part 51 is formed in a cylindrical shape with a metal such as SUS. The introduction part 51 connected to the first pipe part 47 has an introduction port 60 into which exhaust gas from the exhaust manifold 31 is introduced on the inner side.

  The cooling case 61 of the cooling unit 52 is formed in a cylindrical shape with a metal such as SUS. The cooling case 61 is formed with two openings 64 and 65 connected to the cooling water system of the engine 12 via cooling water pipes 62 and 63 (see FIG. 2). A circulation path is formed for drawing water inward and returning water to the cooling water system by the other cooling water pipe 63. The gas pipe 66 of the cooling unit 52 is formed in a straight tube shape with a metal such as SUS, and a plurality of gas pipes 66 are provided in a form extending in parallel with each other in the cooling case 61. Both end portions of each gas pipe 66 are held by the retainers 67 and 68 so as to penetrate the retainers 67 and 68 that cover both end portions of the cooling case 61. As a result, the plurality of first passages 69 formed on the inner sides of the gas pipes 66 are blocked from communicating with the circulation portion of the cooling water in the cooling case 61. A retainer 67 that covers one end portion of the cooling case 61 is connected to the introduction portion 51, and one end portion of the first passage 69 in each gas pipe 66 held by the retainer 67 communicates with the introduction port 60. Each first passage 69 circulates the exhaust gas flowing from the inlet 60 to the one end side toward the other end side. At this time, the exhaust gas passing through each first passage 69 is cooled by the cooling water drawn into the cooling case 61.

  The bypass part 53 is formed of a metal such as SUS and has a cylindrical shape substantially parallel to each gas pipe 66 of the cooling part 52. One end portion of the bypass portion 53 is connected to the introduction portion 51 via the retainer 67, and one end portion of the second passage 70 formed inside by the bypass portion 53 communicates with the introduction port 60. The second passage 70 allows the exhaust gas flowing from the introduction port 60 to the one end side to flow toward the other end side.

As shown in FIGS. 1, 3, and 4, the partition wall 58 is formed in a plate shape with a metal such as SUS and is fixed to the valve support portion 54.
The valve support 54 is formed of a metal such as SUS in a cylindrical shape, and is divided into two inside by a partition wall 58. The valve support 54 forms a third passage 72 and a fourth passage 73 on both sides of the partition wall 58.

  The third passage 72 side of one end portion of the valve support portion 54 is connected to a retainer 68 that covers an end portion of the cooling case 61 opposite to the introduction portion 51, and each gas pipe 66 held by the retainer 68. A downstream end portion of the first passage 69 communicates with the third passage 72. As a result, the cooling passage 75 through which the exhaust gas is circulated is composed of a plurality of first passages 69 and third passages 72, and the third passage 72 forms the outlet portion 72 of the cooling passage 75. Yes. The side walls 76 and 77 of the valve support portion 54 support both ends of the swing shaft 84 of the swing valve 56 through a bearing (not shown) so as to be swingable, and an intermediate portion of the swing shaft 84 is a cooling passage. 75 outlet portions 72 are crossed in the width direction. In the valve support portion 54, a first inclined wall 80 located on the opposite side of the partition wall 58 across the outlet portion 72 of the cooling passage 75 connects the side walls 76 and 77.

  Further, the fourth passage 73 side of the one end portion of the valve support portion 54 is connected to an end portion of the bypass portion 53 opposite to the introduction portion 51 via a retainer 68, and the first end portion in the bypass portion 53 is connected. The downstream end of the second passage 70 communicates with the fourth passage 73. Thus, a bypass passage 81 that bypasses the cooling passage 75 and distributes the exhaust gas is constituted by the second passage 70 and the fourth passage 73, and the fourth passage 73 passes through the outlet 73 of the bypass passage 81. Forming. In the valve support portion 54, a second inclined wall 82 located on the opposite side of the partition wall 58 across the outlet portion 73 of the bypass passage 81 connects the side walls 76 and 77.

  The lead-out part 55 is formed integrally with the valve support part 54 from a metal such as SUS. The cylindrical lead-out portion 55 has a lead-out port 83 on the inner side whose central axis O is substantially perpendicular to the swing shaft 84. The other end portion of the lead-out portion 55 whose one end portion is connected to the second pipe portion 48 is connected to the end portion on the opposite side of the cooling portion 52 and the bypass portion 53 of the valve support portion 54. A lead-out port 83 in the lead-out portion 55 communicates with the passage where the outlet portions 72 and 73 are opened in the cooling passage 75 and the bypass passage 81, and exhaust gas flowing in from the communicated passage in the second pipe portion 48. Derived to the EGR passage.

  In the partition wall 58 of the present embodiment, the end portion 87 located on the downstream side of the exhaust gas flow passing through the cooling passage 75 and the bypass passage 81 is slightly bent toward the cooling passage 75 side. The part to be removed is substantially parallel to the central axis O of the outlet 83. Such a partition wall 58 of this embodiment is offset to the bypass passage 81 side with respect to the central axis O of the outlet 83. In the present embodiment, the first and second inclined walls 80 and 82 connected to one end of the outlet 55 are inclined at substantially the same angle θ with respect to the central axis O of the outlet 83. Further, in the present embodiment, the center lines M and N (see FIG. 4) in the width direction of the cooling passage 75 and the bypass passage 81 are substantially perpendicular to the center axis O of the outlet 83.

  The swing valve 56 is made of a metal such as SUS. The swing shaft 84 of the swing valve 56 extends in the width direction of the outlet portions 72 and 73 of the cooling passage 75 and the bypass passage 81, and particularly in this embodiment, with respect to the central axis O of the outlet 83. It is almost vertical. The valve body 85 of the swing valve 56 is formed in a plate shape that protrudes radially outward from the outer peripheral surface of the swing shaft 84. The protrusion 86 of the swing valve 56 is formed in a plate shape that protrudes radially outward from the outer peripheral surface of the swing shaft 84 in a V-shape with the valve body 85.

The swing valve 56 swings in the valve support portion 54 and the lead-out portion 55 to open and close the outlet portions 72 and 73 of the cooling passage 75 and the bypass passage 81.
Specifically, the valve main body 85 and the protrusion 86 abut against the side walls 76 and 77 of the valve support 54 at any swing position.

  Then, at the first swing position shown in FIG. 5, the valve body 85 is locked to the first inclined wall 80. As a result, the outlet portion 72 of the cooling passage 75 is closed and the outlet portion 73 of the bypass passage 81 is opened, and the high-temperature exhaust gas that has passed through the bypass passage 81 passes through the outlet 83 to the second pipe portion 48. Led. At this time, a slight amount of exhaust gas is allowed to pass between the protrusion 86 and the partition wall 58.

  In the second swing position shown in FIG. 1, the valve main body 85 is locked to the second inclined wall 82 and the downstream end portion 87 of the partition wall 58. As a result, the outlet portion 73 of the bypass passage 81 is closed and the outlet portion 72 of the cooling passage 75 is opened, and the low-temperature exhaust gas cooled by the cooling passage 75 passes to the second pipe portion 48 via the outlet port 83. It is guided.

  Furthermore, as shown in FIG. 6, the valve main body 85 is in any of the first and second inclined walls 80 and 82 and the partition wall 58 at the swing position between the first swing position and the second swing position. Not locked. As a result, the outlet portions 72 and 73 of both the cooling passage 75 and the bypass passage 81 are opened, and the exhaust gas from the passages 75 and 81 merges and mixes at the outlet 83, and the mixed gas flows into the outlet 83. To the second pipe 48. Therefore, when the rocking position of the rocking valve 56 changes between the first rocking position and the second rocking position, the mixing ratio of the exhaust gas from the passages 75 and 81 changes, and the second pipe portion The temperature of the derived gas to 48 changes.

The valve drive unit 57 shown in FIG. 4 is electrically connected to the controller 45 shown in FIG. 2 and adjusts the swing position of the swing valve 56 in accordance with a command from the controller 45.
Based on the detection result of the exhaust gas temperature output from the temperature sensor 44, the controller 45 instructs the valve drive unit 57 about the swing position of the swing valve 56 necessary to achieve the desired exhaust gas temperature. . Therefore, in the engine system 10, the exhaust gas temperature is feedback-controlled. Thus, the temperature adjusting device 42, the temperature sensor 44, and the controller 45 jointly constitute an “EGR control device” described in the claims.

  In the temperature adjusting device 42 of the first embodiment described above, the partition wall 58 that partitions the outlet portion 72 of the cooling passage 75 and the outlet portion 73 of the bypass passage 81 is on the bypass passage 81 side with respect to the central axis O of the outlet port 83. Is offset. Therefore, when both the cooling passage 75 and the bypass passage 81 are opened by the swing valve 56, the exhaust gas from each of the passages 75 and 81 merges asymmetrically with respect to the central axis O at the outlet 83, resulting in turbulent flow. . Due to the occurrence of this turbulent flow, the exhaust gas from each of the passages 75 and 81 is likely to be mixed together at the outlet 83 at the outlet 83, so that the exhaust gas temperature can be accurately detected by the temperature sensor 44. Moreover, in the first embodiment, the swing valve 56 of the temperature adjusting device 42 is swung between the first swing position and the second swing position under the control of the controller 45, so The mixing ratio of the exhaust gas can be freely changed.

According to such a first embodiment, the temperature of the exhaust gas that is merged at the outlet 83 and led to the intake system 20 of the engine 12 can be appropriately feedback controlled. A drop in drivability is prevented.
In the first embodiment, as shown in FIG. 7, the partition wall 58 is offset toward the cooling passage 75 with respect to the central axis O, and the intermediate portion of the swing shaft 84 extends the outlet portion 73 of the bypass passage 81 in the width direction. It may be transformed so as to cross.

(Second embodiment)
FIG. 8 shows a main part of the temperature adjusting device 100 according to the second embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the temperature adjustment device 100, the partition wall 110 is provided on the central axis O of the outlet 83. Further, in the temperature adjusting device 100, the swing shaft 121 of the swing valve 120 extending in the width direction of the outlet portions 72 and 73 of the cooling passage 75 and the bypass passage 81 cools the central axis O of the outlet 83. Offset to the passage 75 side. That is, in the present embodiment, the center axis P of the swing shaft 121 and the center axis O of the outlet 83 are in a torsional positional relationship.

As described above, in the temperature adjustment device 100 of the second embodiment, the swing shaft 121 is offset toward the cooling passage 75 side with respect to the central axis O of the outlet 83. Therefore, when both the cooling passage 75 and the bypass passage 81 are opened by the swing valve 120, the exhaust gas from each of the passages 75 and 81 passes along the valve body 85 of the swing valve 120 at the outlet 83. O is merged asymmetrically and becomes turbulent. Therefore, the exhaust gases from the passages 75 and 81 are likely to be mixed together with the merge, so that the temperature of the exhaust gas guided to the intake system 20 of the engine 12 can be appropriately feedback-controlled also by the second embodiment.
In the second embodiment, the swing shaft 121 is offset toward the bypass passage 81 with respect to the central axis O, and the intermediate portion of the swing shaft 121 crosses the outlet portion 73 of the bypass passage 81 in the width direction. It may be deformed.

(Third embodiment)
FIG. 9 shows a main part of the temperature adjusting device 150 according to the third embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the temperature adjustment device 150, the swinging shaft 161 of the swinging valve 160 extending in the width direction of the outlet portions 72 and 73 of the cooling passage 75 and the bypass passage 81 is connected to the bypass passage 81 with respect to the central axis O of the outlet 83. Offset to the side. In other words, in the present embodiment, the central axis P of the swing shaft 161 and the central axis O of the outlet 83 are in a torsional position relationship. The partition wall 58 is offset toward the bypass passage 81 with respect to the central axis O as in the first embodiment.

  As described above, in the temperature adjustment device 150 of the third embodiment, the swing shaft 161 in addition to the partition wall 58 is offset toward the bypass passage 81 with respect to the central axis O of the outlet 83. Therefore, when both the cooling passage 75 and the bypass passage 81 are opened by the rocking valve 160, the exhaust gas from each of the passages 75 and 81 passes along the valve body 85 of the rocking valve 160 at the outlet 83. O is merged asymmetrically and the turbulence effect is enhanced. Therefore, the exhaust gases from the passages 75 and 81 are easily mixed together with the merge, so that the temperature of the exhaust gas guided to the intake system 20 of the engine 12 can be appropriately feedback-controlled also by the third embodiment.

  In the third embodiment, the swing shaft 161 may be modified to be offset from the central axis O toward the cooling passage 75 and the partition wall 58 may be offset toward the bypass passage 81. Alternatively, the swing shaft 161 is offset to the bypass passage 81 side and the partition wall 58 is offset to the cooling passage 75 side with respect to the central axis O, and the intermediate portion of the swing shaft 161 widens the outlet portion 73 of the bypass passage 81. You may deform | transform so that it may cross in a direction. Alternatively, both the swing shaft 161 and the partition wall 58 are offset toward the cooling passage 75 with respect to the central axis O, and the intermediate portion of the swing shaft 161 is deformed so as to cross the outlet portion 73 of the bypass passage 81 in the width direction. May be.

(Fourth embodiment)
FIG. 10 shows a main part of the temperature adjustment device 200 according to the fourth embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the temperature adjusting device 200, the rocking valve 210 is swung from the outer peripheral edge 212 of the valve main body 211 to the first rocking position side and from the one plate surface 214 of the valve main body 211 to the second rocking. It has the 2nd protrusion part 215 which protrudes to a position side. The first protrusion 213 has a bowl shape that continuously extends in the circumferential direction along the outer peripheral edge 212 of the valve body 211, and the plate surface 216 of the valve body 211 on the side opposite to the second protrusion 215. A substantially vertical protruding end is formed. Each second protrusion 215 is formed in a plate shape substantially parallel to the swing shaft 84 and substantially perpendicular to the plate surface 214 of the valve body 211.

  In such a temperature control device 200 of the fourth embodiment, when the exhaust gas flows from the cooling passage 75 opened by the swing valve 210 to the outlet 83, the first temperature is projected from the valve body 211 to the first swing position side. The exhaust gas collides with the one protrusion 213, and a turbulent flow is generated. Further, in the temperature adjusting device 200, when the exhaust gas flows from the bypass passage 81 opened by the swing valve 210 to the outlet 83, the exhaust gas is exhausted from the valve body 211 to the second protrusion 215 that protrudes toward the second swing position. Turbulence occurs when the gas collides. As described above, when both the cooling passage 75 and the bypass passage 81 are opened, the exhaust gas from the passages 75 and 81 that has become turbulent due to the action of the first and second protrusions 213 and 215 at the outlet 83. It becomes easy to mix with the merge. Therefore, according to the fourth embodiment, the temperature of the exhaust gas led to the intake system 20 of the engine 12 can be appropriately feedback controlled.

  In the fourth embodiment, as shown in FIG. 11, the first protrusion 213 protrudes from the valve body 211 toward the second swing position, and the second protrusion 215 extends from the valve body 211 to the first swing position. You may deform | transform so that it may protrude to the side. Alternatively, as shown in FIG. 12, the first and second protrusions 213 and 215 are moved to the same swing position side of the first and second swing positions (FIG. 12 is an example of the first swing position side). You may deform | transform so that it may protrude. Alternatively, as shown in FIG. 13, first and second protrusions 213 and 215 projecting from the valve body 211 to the first swing position side, and first and second protrusions projecting from the valve body 211 to the second swing position side. You may deform | transform so that the two protrusions 213 and 215 may be provided.

Moreover, about the 1st protrusion 213, you may deform | transform into the shape divided | segmented into plurality in the circumferential direction of the valve main body 211, and about the number of the 2nd protrusions 215, it can change suitably.
In addition, the fourth embodiment described above or the modification thereof may be modified so as to have at least one characteristic configuration of the second or third embodiment or the modification thereof.

(Fifth embodiment)
FIG. 14 shows a main part of a temperature adjustment device 250 according to the fifth embodiment of the present invention. Components that are substantially the same as those of the third embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the temperature adjustment device 250, the first and second inclined walls 261 and 262 of the valve support portion 260 are inclined at different angles θ ₁ and θ _{2 with} respect to the central axis O of the outlet 83. In this embodiment, as in the third embodiment, the swing shaft 161 and the partition wall 58 of the swing valve 160 are offset toward the bypass passage 81 with respect to the central axis O, and the flow passage area is reduced. The inclination angle θ ₂ of the second inclined wall 262 on the bypass passage 81 side is larger than the inclination angle θ ₁ of the first inclined wall 261.

As described above, in the temperature adjustment device 250 of the fifth embodiment, the inclination angles θ ₁ and θ ₂ of the first and second inclined walls 261 and 262 with respect to the central axis O of the outlet 83 are different. For this reason, when both the cooling passage 75 and the bypass passage 81 are opened by the swing valve 160, the exhaust gas from the cooling passage 75 and the bypass passage 81 passes through the first inclined wall 261 and the second inclined wall at the outlet 83. 262 and asymmetrical merging with respect to the central axis O, resulting in turbulent flow. Therefore, the exhaust gases from the passages 75 and 81 are easily mixed together with the merge, so that the temperature of the exhaust gas guided to the intake system 20 of the engine 12 can be appropriately feedback-controlled also by the fifth embodiment.

In the fifth embodiment, the first inclined wall 261 may be modified such that the inclination angle θ ₁ is larger than the inclination angle θ ₂ of the second inclined wall 262.
Moreover, you may deform | transform about 5th embodiment demonstrated above or its modification so that it may have at least one characteristic structure of 1st, 2nd, 4th embodiment or those modifications.

(Sixth embodiment)
FIG. 15 shows a main part of a temperature adjustment device 300 according to the sixth embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the valve support portion 310 of the temperature adjusting device 300, the connecting portions 311a and 312a with the retainer 68 on the side walls 311 and 312 supporting the swing shaft 84 are displaced in the opposite direction of the side walls 311 and 312 compared to other portions. ing. As a result, the communication side with the first passage 69 of the third passage 72 that is the outlet portion 72 of the cooling passage 75 is offset in the width direction with respect to the central axis O of the outlet 83, thereby forming the offset portion 320. is doing. In FIG. 15, the alternate long and short dash line Q represents the center line in the width direction of the offset portion 320, and the alternate long and short dash line M represents the center line in the width direction of the portion of the third passage 72 excluding the offset portion 320.

  In such a temperature control device 300 of the sixth embodiment, the exhaust gas from each of the passages 75 and 81 is introduced into the outlet 83 when both the cooling passage 75 and the bypass passage 81 are opened by the swing valve 56. Asymmetrical merging with respect to the central axis O of the outlet 83 results in turbulent flow. Therefore, the exhaust gases from the passages 75 and 81 are likely to be mixed together with the merging, so that the temperature of the exhaust gas guided to the intake system 20 of the engine 12 can be appropriately feedback controlled also by the sixth embodiment.

In the sixth embodiment, as shown in FIG. 16, the communication side with the second passage 70 of the fourth passage 73 that is the outlet portion 73 of the bypass passage 81 is offset in the width direction with respect to the central axis O. You may deform | transform so that the offset part 322 may be formed. Or you may deform | transform so that the offset part 320 of the cooling passage 75 like the above-mentioned 6th embodiment and the offset part 322 of the bypass passage 81 like the modification of FIG. 16 may be formed together. However, in this case, the offset direction with respect to the central axis O may be the same in the offset part 320 and the offset part 322, or may be different from each other.
Moreover, you may deform | transform about 6th embodiment described above or its modification so that it may have at least one characteristic structure of 2nd-5th embodiment or those modifications.

(Seventh embodiment)
FIG. 17 shows a main part of a temperature adjustment device 350 according to the seventh embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
The temperature adjustment device 350 includes a first flow blocking member 370 and a second flow blocking member 371 that protrude from the inner wall surface 361 of the valve support portion 360 into the cooling passage 75 and the outlet portions 72 and 73 of the bypass passage 81, respectively. Yes. The first current blocking member 370 and the second current blocking member 371 are provided so as to face each other with the partition wall 362 of the valve support portion 360 interposed therebetween. The first current blocking member 370 is formed in a plate shape substantially parallel to the swing shaft 84, and is inclined toward the downstream side of the exhaust gas flow in the cooling passage 75 with respect to the inner wall surface 361. Similarly, the second current blocking member 371 is formed in a plate shape substantially parallel to the swing shaft 84 and is inclined toward the downstream side of the exhaust gas flow in the bypass passage 81 with respect to the inner wall surface 361. Yes.

  The temperature adjusting device 350 further includes a third current blocking member 372 and a fourth current blocking member 373 that protrude from the both plate surfaces 363 and 364 of the partition wall 362 into the outlet portions 72 and 73 of the cooling passage 75 and the bypass passage 81, respectively. I have. The third current blocking member 372 and the fourth current blocking member 373 are provided so as to sandwich the partition 362. The third current blocking member 372 is formed in a plate shape substantially parallel to the swing shaft 84, and is inclined toward the downstream side of the exhaust gas flow in the cooling passage 75 with respect to the plate surface 363. Similarly, the fourth current blocking member 373 is formed in a plate shape substantially parallel to the swing shaft 84, and is inclined toward the downstream side of the exhaust gas flow in the bypass passage 81 with respect to the plate surface 364. Yes.

  As described above, in the temperature adjustment device 350 of the seventh embodiment, the first and third flow shielding members 370 and 372 are provided in the outlet portion 72 of the passage 75 so as to block the exhaust gas flow in the cooling passage 75. . Therefore, at the outlet 72 of the cooling passage 75, the exhaust gas flow collides with the first and third current blocking members 370 and 372 and becomes turbulent. Further, in the temperature adjustment device 350, second and fourth flow blocking members 371 and 373 are provided in the outlet portion 73 of the passage 81 so as to block the flow of exhaust gas in the bypass passage 81. Therefore, at the outlet 73 of the bypass passage 81, the flow of the exhaust gas collides with the second and fourth current blocking members 371 and 373 and becomes a turbulent flow. As described above, in the outlet 83 when both the cooling passage 75 and the bypass passage 81 are opened by the swing valve 56, the exhaust from the passages 75 and 81 turbulent due to the action of the current blocking members 370 to 373. It becomes easy for gas to mix with merging. Therefore, according to the seventh embodiment as well, the temperature of the exhaust gas led to the intake system 20 of the engine 12 can be appropriately feedback controlled.

In the seventh embodiment, at least one of the first and second current blocking members 370 and 371 may be deformed into a shape that is substantially perpendicular to the inner wall surface 361 of the valve support portion 360, or the inner You may deform | transform into the shape which inclines to the upstream of an exhaust gas flow with respect to the wall surface 361. FIG. In addition, the third and fourth current shielding members 372 and 373 may be deformed into a shape substantially perpendicular to the corresponding plate surface 363 or 364 of the partition wall 362, or the plate surface 363 or 364 may be changed to the plate surface 363 or 364. On the other hand, you may deform | transform into the shape which inclines to the upstream of an exhaust gas flow. Furthermore, you may deform | transform so that any one type-three types may be provided among the current blocking members 370-373. Furthermore, the number and position of the various flow blocking members 370 to 373 in the corresponding passage 75 or 81 can be changed as appropriate.
In addition, the seventh embodiment described above or a modification thereof may be modified so as to have at least one characteristic configuration of the second to sixth embodiments or a modification thereof.

(Eighth embodiment)
FIG. 18 shows a main part of the temperature adjustment device 400 according to the eighth embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
The temperature adjusting device 400 includes a current blocking member 420 that protrudes into the outlet 83 from the inner wall surface 411 of the outlet 410. The two current blocking members 420 are provided in a form in which the first inclined wall 80 and the second inclined wall 82 face each other in the direction sandwiching the central axis O of the outlet 83. Each of the current blocking members 420 is formed in a plate shape substantially parallel to the swing shaft 84, and is inclined toward the downstream side of the exhaust gas flow at the outlet 83 with respect to the inner wall surface 411.

  As described above, in the temperature adjustment device 400 of the eighth embodiment, the flow blocking member 420 is disposed in the outlet 83 so as to block the exhaust gas flow in the outlet 83. Therefore, when both the cooling passage 75 and the bypass passage 81 are opened by the swing valve 56, the exhaust gas flow from the passages 75, 81 collides with the flow blocking member 420 at the outlet 83 and becomes turbulent flow. Join together. Therefore, the exhaust gases from the passages 75 and 81 are likely to be mixed together with the merging, so that the temperature of the exhaust gas guided to the intake system 20 of the engine 12 can be appropriately feedback controlled also by the eighth embodiment.

In the eighth embodiment, the current blocking member 420 may be deformed into a plate shape that is substantially perpendicular to the inner wall surface 411, or may be inclined toward the upstream side of the exhaust gas flow with respect to the inner wall surface 411. You may deform | transform into. In addition, the number and position of the current blocking members 420 in the outlet 83 can be changed as appropriate.
In addition, the eighth embodiment described above or its modification may be modified so as to have at least one characteristic configuration of the second to seventh embodiments or their modifications.

It is sectional drawing which shows the principal part of the temperature control apparatus by 1st embodiment. It is a mimetic diagram showing an engine system by a first embodiment. It is a partially notched front view which shows the temperature control apparatus by 1st embodiment. It is a side view which shows the principal part of the temperature control apparatus by 1st embodiment. It is sectional drawing for demonstrating the action | operation of the temperature control apparatus by 1st embodiment. It is sectional drawing for demonstrating the action | operation of the temperature control apparatus by 1st embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by the modification of 1st embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by 2nd embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by 3rd embodiment. It is sectional drawing (A) which shows the principal part of the temperature control apparatus by 4th embodiment, and the top view (B) which shows the rocking | fluctuation valve by 4th embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by the modification of 4th embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by the modification of 4th embodiment, and the top view (B) which shows the swing valve by the same modification of 4th embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by the modification of 4th embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by 5th embodiment. It is the side view (A) and sectional drawing (B) which show the principal part of the temperature control apparatus by 6th embodiment. It is the side view (A) and sectional drawing (B) which show the principal part of the temperature control apparatus by the modification of 6th embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by 7th embodiment. It is sectional drawing which shows the principal part of the temperature control apparatus by 8th embodiment.

Explanation of symbols

10 engine system, 12 engine, 20 intake system, 30 exhaust system, 40 EGR system, 42, 100, 150, 200, 250, 300, 350, 400 Temperature adjusting device (EGR control device), 44 Temperature sensor (EGR control device) ), 45 controller (EGR control device), 51 introduction part, 52 cooling part, 53 bypass part, 54, 260, 310, 360 valve support part, 55, 410 lead-out part, 56, 120, 160, 210 swing valve, 57 valve drive unit, 58, 110, 362 partition wall, 60 inlet, 61 cooling case, 66 gas pipe, 69 first passage (cooling passage), 70 second passage (bypass passage), 72 third passage, outlet portion ( Cooling passage), 73 fourth passage, outlet (bypass passage), 75 cooling passage, 80, 261 first inclined wall, 81 bypass passage, 82, 262 first Inclined wall, 83 Outlet, 84, 121, 161 Oscillating shaft, 85, 211 Valve body, 86 Protruding part, 212 Outer peripheral edge part, 213 First projecting part, 215 Second projecting part, 320, 322 Offset part, 370 First current blocking member, 371 Second current blocking member, 372 Third current blocking member, 373 Fourth current blocking member, 420 Current blocking member, O center axis, θ, θ ₁ , θ ₂ inclination angle

Claims (8)

An exhaust gas recirculation control device that controls the temperature of exhaust gas that is recirculated by being led to an intake system of an internal combustion engine,
A cooling passage for circulating the exhaust gas while cooling,
A bypass passage that bypasses the cooling passage and distributes exhaust gas;
A partition partitioning the outlet portion of the cooling passage and the outlet portion of the bypass passage;
In the first swing position, the outlet portion of the cooling passage is closed and the outlet portion of the bypass passage is opened. In the second swing position, the outlet portion of the cooling passage is opened and the outlet portion of the bypass passage is closed. A swing valve that opens both outlets of the cooling passage and the bypass passage between a swing position and the second swing position;
An outlet for communicating exhaust gas to the intake system, communicating with a passage having an outlet portion open among the cooling passage and the bypass passage;
The exhaust gas recirculation control device according to claim 1, wherein the partition wall is offset toward the cooling passage side or the bypass passage side with respect to a central axis of the outlet port. An exhaust gas recirculation control device that controls the temperature of exhaust gas that is recirculated by being led to an intake system of an internal combustion engine,
A cooling passage for circulating the exhaust gas while cooling,
A bypass passage that bypasses the cooling passage and distributes exhaust gas;
A partition partitioning the outlet portion of the cooling passage and the outlet portion of the bypass passage;
In the first swing position, the outlet portion of the cooling passage is closed and the outlet portion of the bypass passage is opened. In the second swing position, the outlet portion of the cooling passage is opened and the outlet portion of the bypass passage is closed. A swing valve that opens both outlets of the cooling passage and the bypass passage between a swing position and the second swing position;
An outlet for communicating exhaust gas to the intake system, communicating with a passage having an outlet portion open among the cooling passage and the bypass passage;
The swing valve has a swing shaft extending in a width direction of the cooling passage and the bypass passage,
The exhaust gas recirculation control device according to claim 1, wherein the swing shaft is offset toward the cooling passage or the bypass passage with respect to a central axis of the outlet. An exhaust gas recirculation control device that controls the temperature of exhaust gas that is recirculated by being led to an intake system of an internal combustion engine,
A cooling passage for circulating the exhaust gas while cooling,
A bypass passage that bypasses the cooling passage and distributes exhaust gas;
A partition partitioning the outlet portion of the cooling passage and the outlet portion of the bypass passage;
In the first swing position, the outlet portion of the cooling passage is closed and the outlet portion of the bypass passage is opened. In the second swing position, the outlet portion of the cooling passage is opened and the outlet portion of the bypass passage is closed. A swing valve that opens both outlets of the cooling passage and the bypass passage between a swing position and the second swing position;
An outlet for communicating exhaust gas to the intake system, communicating with a passage having an outlet portion open among the cooling passage and the bypass passage;
The oscillating valve has a plate-like valve main body and a protrusion protruding from the valve main body to at least one side of the first oscillating position and the second oscillating position. Circulation control device.   The exhaust gas recirculation control device according to claim 3, wherein the swing valve has the flange-shaped protrusion formed along the outer peripheral edge of the valve body. An exhaust gas recirculation control device that controls the temperature of exhaust gas that is recirculated by being led to an intake system of an internal combustion engine,
A cooling passage for circulating the exhaust gas while cooling,
A bypass passage that bypasses the cooling passage and distributes exhaust gas;
A partition partitioning the outlet portion of the cooling passage and the outlet portion of the bypass passage;
In the first swing position, the outlet portion of the cooling passage is closed and the outlet portion of the bypass passage is opened. In the second swing position, the outlet portion of the cooling passage is opened and the outlet portion of the bypass passage is closed. A swing valve that opens both outlets of the cooling passage and the bypass passage between a swing position and the second swing position;
A lead-out port that communicates with a passage in which an outlet portion is opened among the cooling passage and the bypass passage, and leads exhaust gas to the intake system;
A first inclined wall provided on the opposite side of the partition across the outlet portion of the cooling passage, and inclined with respect to the central axis of the outlet port;
A second inclined wall provided on the opposite side of the partition across the outlet portion of the bypass passage, and inclined with respect to the central axis,
The exhaust gas recirculation control device according to claim 1, wherein an inclination angle of the first inclined wall with respect to the central axis is different from an inclination angle of the second inclined wall with respect to the central axis. An exhaust gas recirculation control device that controls the temperature of exhaust gas that is recirculated by being led to an intake system of an internal combustion engine,
A cooling passage for circulating the exhaust gas while cooling,
A bypass passage that bypasses the cooling passage and distributes exhaust gas;
A partition partitioning the outlet portion of the cooling passage and the outlet portion of the bypass passage;
In the first swing position, the outlet portion of the cooling passage is closed and the outlet portion of the bypass passage is opened. In the second swing position, the outlet portion of the cooling passage is opened and the outlet portion of the bypass passage is closed. A swing valve that opens both outlets of the cooling passage and the bypass passage between a swing position and the second swing position;
An outlet for communicating exhaust gas to the intake system, communicating with a passage having an outlet portion open among the cooling passage and the bypass passage;
At least one of the cooling passage and the bypass passage has an offset portion that is offset in the width direction of the cooling passage and the bypass passage with respect to the center axis of the outlet port.   7. The apparatus according to claim 1, further comprising a flow blocking member that is provided in at least one of the outlet portion of the cooling passage and the outlet portion of the bypass passage and blocks the flow of exhaust gas. Exhaust gas recirculation control device. The exhaust gas recirculation control device according to any one of claims 1 to 7, further comprising a flow blocking member provided in the outlet and configured to block a flow of exhaust gas.

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