JP5782728B2 - Intake structure of internal combustion engine - Google Patents

Description

  The present invention relates to an intake structure for an internal combustion engine.

  The two manifold arrays formed with a plurality of intake paths gather on the upstream side of the intake flow and separate on the downstream side to distribute the intake air to the intake ports of the two banks via the intake path, and from outside the intake path In an intake manifold of an internal combustion engine having an intake passage gas introduction device for introducing gas into the intake passage, the intake passage gas introduction device is arranged in the arrangement direction of the manifold arrangement by surrounding a space in a separation portion of the two manifold arrangements. A manifold arrangement on the separation side having a formed gas introduction path and a gas branch path that branches from the gas introduction path for each intake path and opens to the intake path downstream of the gas introduction path in the intake path. An intake manifold is known that is connected to a cylinder head via a flange formed at the front end portion (Patent Document 1).

JP 2009-287418 A

  However, in the configuration of the intake manifold, since the rigidity of the flange and the joint portion between the downstream intake path and the flange is not high, when the intake manifold and the cylinder head are fastened by a plurality of bolts at the outer edge portion of the flange, There is a problem that the extension distance of the joint surface between the bolts becomes longer on the side between the banks, and the unevenness of the surface pressure distribution on the fastening surface between the flange and the cylinder head increases.

  The problem to be solved by the present invention is to provide an intake structure for an internal combustion engine that can suppress unevenness of the surface pressure distribution on the fastening surface between the flange of the intake manifold and the cylinder head.

According to the present invention, the gas flow path for introducing a part of the combustion gas into the intake flow path is provided in the first wall portion on the bolt side among the wall portions of the intake flow path, and is formed by the groove of the flange. To solve.

  According to the present invention, since the rigidity of the outer wall portion and the flange of the intake flow path is increased by the gas flow path, even when the flange and the cylinder head are fastened by bolts or the like provided outside the multiple intake flow paths. In addition, it is possible to suppress unevenness of the surface pressure distribution on the fastening surface on the side between the banks.

1 is a perspective view of an intake manifold and a cinder head of an internal combustion engine according to an embodiment of the present invention. It is a perspective view of the cylinder head of FIG. It is a perspective view of the intake manifold of FIG. FIG. 2 is a bottom view of the intake manifold of FIG. 1. It is sectional drawing which follows the VV line of FIG. It is sectional drawing which follows the VI-VI line of FIG. It is sectional drawing which follows the VII-VII line of FIG. It is sectional drawing which follows the VIII-VIII line of FIG. It is an enlarged view of the part enclosed by the IX line of FIG. FIG. 9 is an enlarged cross-sectional view (corresponding to FIG. 9) of an intake passage of an intake manifold of an internal combustion engine according to another embodiment of the present invention. FIG. 10 is an enlarged cross-sectional view (corresponding to FIG. 9) of an intake passage of an intake manifold of an internal combustion engine according to still another embodiment of the present invention. It is a figure which shows a part of bottom view of the intake manifold of FIG. FIG. 10 is an enlarged cross-sectional view (corresponding to FIG. 9) of an intake passage of an intake manifold of an internal combustion engine according to still another embodiment of the present invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

<< First Embodiment >>
1 is a perspective view of an intake manifold 100 and a cylinder head 200 to which an intake structure for an internal combustion engine according to an embodiment of the present invention is applied. FIG. 2 is a perspective view of the cylinder head 200. FIG. It is a perspective view. The intake manifold 100 of this example is a manifold of a V-type 6-cylinder internal combustion engine (hereinafter also referred to as an engine), and the cylinder head 200 corresponds to the cylinder head of the left bank. Although not shown, there is a cylinder head in the right bank as well as the left bank, which is connected to the intake manifold 100 of this example. The intake manifold 100 is made of, for example, resin.

  As shown in FIGS. 1 to 3, the intake manifold 100 is provided at a position above the engine body in the center between the banks, and includes intake passages 11 to 16, flanges 21 to 23, a lid portion 31, and the like. It has. The intake manifold 100 is connected by a flange 21 to an intake collector (not shown) and a branch (not shown) on the intake system side, and the flange 21 is provided with a fastening hole 21a for fastening with the manifold by bolts. Yes. The intake manifold 100 is connected to the cylinder head 200 of the right bank by a flange 22 and is connected to the cylinder head 200 of the left bank by a flange 23. The flange 22 is provided with a fastening hole 22a for fastening with the cylinder head 200 of the right bank by a bolt 22b. The flange 23 is provided with a fastening hole 23a for fastening with the cylinder head 200 of the left bank by a bolt 23b. Further, the flange 22 and the fastening hole 22a, and the flange 23 and the fastening hole 23a are provided outside the wall portions of the respective intake passages 11 to 16 described later, and the intake passages 11 to 11 that cannot be fastened with bolts. It is not provided on the side between 16 banks.

  The manifold branches on the intake collector side are aggregated by the flange 21 and connected to the intake flow paths 11 to 16, respectively. The intake flow paths 11 to 16 are connected to each cylinder. The left bank intake passages 11, 13, and 15 communicate with the intake ports 201, 203, and 205 of the left bank cylinder head 200, and the right bank intake passages 12, 14, and 16 correspond to the cylinder heads of the right bank. Each communicates with the intake port. As a result, outside air drawn from the intake collector passes through the intake passages 11 to 16 and is supplied to the intake port of each cylinder.

  The intake passages 11, 13, and 15 are connected in the cylinder row direction for each cylinder, and the intake passages 12, 14, and 16 are connected in the cylinder row direction for each cylinder. In addition, the intake flow paths 11 to 16 are such that the intake flow paths 11, 13, 15 and the intake flow paths 12, 14, 16 move away from the flange 21 on the upstream side toward the flanges 22, 23 on the downstream side. Is formed. Thereby, when viewed from the cylinder row direction, the intake manifold 100 has a shape that widens toward the engine body from the flange on the intake collector side that is connected to the flange 21.

  The lid portion 31 covers a part of the side surface of the intake manifold 100 and constitutes a part of a wall portion of an EGR pipe 41 described later. Similarly, the right bank of the intake manifold 100 is also provided with a lid portion 32 which will be described later, and the lid portion 32 constitutes a part of a wall portion of an EGR pipe 42 which will be described later.

  Further, the cylinder head 200 is provided with a fuel injection valve 210 on a side surface of the cylinder head 200 so as to directly inject fuel into each cylinder from the side of the combustion chamber. The intake structure of this example is not limited to a direct injection engine.

  Next, detailed configurations of the intake passages 11 to 16, the lid portions 31 and 32, and the EGR pipes 40, 41 and 42 will be described with reference to FIGS. 4 to 9. 4 is a bottom view of the intake manifold 100, and FIG. 5 is a cross-sectional view taken along the line V-V in FIG. 6 is a perspective view taken along line VI-VI in FIG. 3, FIG. 7 is a perspective view taken along line VII-VII in FIG. 3, and FIG. 8 is a line VIII-VIII in FIG. FIG. 9 is an enlarged view of a dotted line part IX in FIG. 8.

  The intake manifold 100 of this example is provided with EGR pipes 40, 41 and 42. The EGR pipes 40, 41 and 42 recirculate a mixed gas (hereinafter referred to as EGR gas) by blow-by gas or EGR, which is a part of engine combustion gas, from the exhaust branch of the exhaust passage and into the intake air. It is a flow path for supplying, and is connected to each intake flow path 11-16.

  An opening 40a that opens toward the bottom surface side of the intake manifold 100 is formed at one end of the EGR pipe 40, and EGR gas that flows in from the exhaust branch is supplied to the EGR pipe 40 from the opening 40a. The opening 40 a is provided at the position of the branch point of the EGR pipe 40 when viewed from the bottom surface side of the intake manifold 100. The other end of the EGR pipe 40 is branched at a central portion between the row of the intake flow paths 11, 13, 15 and the row of the intake flow paths 11, 13, 15 and communicates with the EGR pipe 41 and the EGR pipe 42.

  The EGR pipe 41 includes a wall portion 111, 131, 151 on the bolt 23b side among the side walls of the intake channels 11, 13, 15 of the left bank, a wall portion 171 that connects the wall portion 111 and the wall portion 131, and It is formed by a wall portion 172 that connects the wall portion 131 and the wall portion 151. The EGR pipe 42 includes walls 121, 141, 161 on the bolt 22b side of the side walls of the intake channels 12, 14, 16 of the right bank, a wall 181 connecting the wall 121 and the wall 141, In addition, a wall portion 182 connecting the wall portion 141 and the wall portion 161 is formed.

  As a result, the EGR gas passes through the EGR pipe 40 from the bottom surface side of the intake manifold 100 (from the flanges 22 and 23 side) and passes through the central portion of the intake flow channels 11, 13, 15 and the intake flow channels 12, 14, 16. The intake air flow path 11 passes through an EGR pipe 41 provided between the intake flow path 13 and the intake flow path 15 and an EGR pipe 42 provided between the intake flow path 14 and the intake flow path 16. Through 16 outside EGR pipe 41 and EGR pipe 42, respectively, and is supplied to each intake flow path 11-16.

  Hereinafter, the configuration of the portion where the EGR gas flows from the EGR pipe 41 to the intake passage 13 will be described with reference to FIGS. 6 to 9, but the other intake passages 11, 12, 14 to 16 and the EGR pipe 41 will be described. , 42 is the same.

  The EGR pipe 41 is parallel to the cylinder row direction and is formed along the wall portion 170, the EGR pipe 41a, the EGR pipe 41b formed so as to be parallel to the intake flow path 13, and the bottom surface of the flange 23. And an EGR pipe 41c formed so as to be parallel to each other. On the side surface on the bolt 23a side of the intake manifold 100, the wall 131a and the wall 131b, which are part of the wall 131, are formed so that the thickness is larger than the thickness of the other wall 131c, and the thickness is large. On the side surface of the wall 131a on the bolt side, a concave portion that is recessed toward the intake flow path 13 is formed. And the said recessed part becomes a side wall of the EGR pipe | tube 41a. The lid portion 31 is joined to the wall portion 131a from the side surface of the intake manifold 100 on the bolt 23a side so as to cover the concave portion. And the part which covers the said recessed part among the cover parts 31 becomes a side wall of the EGR pipe | tube 41a.

The EGR pipe 41 b is bent from the EGR pipe 41 a so that the pipe extends into the flange 23. That is, the EGR pipe 41b is formed by providing a pipe penetrating the wall 131b. The area of the cross section in the direction perpendicular to the axial direction of the EGR pipe 41b is smaller than the area of the cross section of the EGR pipe 41a. The thickness of the wall portion 131b which is a part of the EGR pipe 41b (corresponding to _{d 1} in FIG. 7), so as not to be part of the EGR pipe 41, in other words, the wall portion 131c which is not bonded to the EGR pipe 41 the thickness of the (corresponding to d ₂ in FIG. 7) from the larger as the wall portion 131 is formed. A groove is formed in a part of the bottom surface 23c of the flange 23. The groove is formed so that the EGR pipe 41b and the intake passage 13 communicate with each other, and the groove serves as the EGR pipe 41c. Since the bottom surface 23 c of the flange 23 comes into contact with the cylinder head 200 of the left bank, the groove is covered with the cylinder head 200. EGR pipe 41c is made form the groove and the cylinder head 200 provided on the bottom surface 23c of the flange 23.

  As described above, in this example, the EGR pipe 41 provided on the walls 111, 131, 151 and joined to the flange 23, and the EGR pipe provided on the walls 121, 141, 161 and joined to the flange 22 are used. 42. As a result, the rigidity of the outer wall portions of the intake flow paths 11 to 16 and the flanges 22 and 23 increases, and the entire flange portion forms a highly rigid frame. When it is fastened to the cylinder head 200 through a plurality of bolts at a portion, it is possible to suppress the unevenness of the surface pressure distribution on the fastening surface which is the bottom surface of the flange 22 even on the side between the banks.

  Further, in the V-type multi-cylinder internal combustion engine, the branch and collector, which serve as air flow paths, and the intake manifold 100 are divided. Therefore, a fastening hole 21 a that is fastened by a bolt is provided at the outer edge of the flange 21. ing. The intake manifold 100 is also fastened to the cylinder head 200 of the left bank and the cylinder head of the right bank by bolts, so that fastening holes 22a and 23a are provided at outer edge portions of the flanges 22 and 23. Here, when the intake manifold 100 is viewed in a plan view, the fastening holes 22a and the fastening holes 23a are disposed outside the fastening holes 21a so as to avoid the fastening holes 21a. Therefore, the bolt fastening holes 22a and 23a are arranged closer to the outer side on the plane of the flanges 22 and 23. In this case, if the intake manifold 100 and the cylinder head 200 are fastened by the bolts 22b and 23b, the surface pressure is applied to the outside on the plane of the flanges 22 and 23, and the surface pressure distribution may be biased.

  In this example, since the EGR pipe 41 and the EGR pipe 42 are provided as described above, rigidity is increased at the outer edge portions on the planes of the flanges 22 and 23, so that pressure is applied to the outer edge portions when fastening with bolts. Even when the pressure is concentrated, the unevenness of the surface pressure distribution can be reduced.

  Further, in this example, the wall of the EGR pipe 41 so that the thickness of the wall 131b that is a part of the downstream EGR pipe 41b is larger than the thickness of the wall 131c that is not joined to the EGR pipe 41. A portion 131 is formed. Thus, when the intake manifold 100 and the cylinder head 200 are fastened by the bolts 22b and 23b, the axial force of the bolt can be efficiently transmitted to the fastening surface.

  Further, in this example, the EGR pipe 41 in the left bank and the EGR pipe 42 in the right bank are connected at the central portion between the row of the intake flow channels 11, 13, 15 and the row of the intake flow channels 12, 14, 16. Has been. Thereby, in the intake manifold 100, since it is not necessary to provide a plurality of opening holes 40a that are inlets for the air supplied from the branch, the structure can be simplified. Moreover, the flow path 41 and the flow path 42 can be shape | molded with a metal mold | die. Further, by branching the EGR pipe 40 into the EGR pipe 41 and the EGR pipe 42, the stress applied to the EGR pipes 40 to 42 can be relaxed. In addition, a difference in flow rate generated between the EGR pipe 41 and the EGR pipe 42 can be suppressed.

  This example also includes a fuel injection valve 210 that injects fuel directly into the cylinder from the side of the combustion chamber. In this example, since it is not always necessary to provide an EGR pipe along the wall portion in the hollow portion formed between the intake flow channels 11, 13, 15 and the intake flow channels 12, 14, 16, the flange 22, 23 may not extend to the hollow portion. For this reason, when the fuel injection valve 210 is provided at a position where fuel is directly injected into the cylinder from the side of the combustion chamber, the fastening surface of the cylinder head 200 with the flange 22 is designed to be the fuel injection valve 210. Can be prevented from interfering with. Moreover, when processing the insertion hole of the fuel injection valve 210, it can prevent that a processing tool interferes with the said fastening surface. As a result, the degree of freedom in designing the cylinder head 200 can be increased.

  In this example, the EGR pipe 41 c is configured by a groove formed in the flange 23. Thereby, since the EGR pipe | tube 41c can be shape | molded with a metal mold | die, manufacturing cost can be held down. In this example, the EGR pipe 41c is configured by a groove formed in the flange 23, but may be configured by forming a groove on a fastening surface with the flange 23 on the cylinder head 200.

  The EGR pipes 40, 41, and 42 in this example correspond to the “gas flow path” of the present invention, the wall 131a corresponds to the “first wall”, and the wall 131b corresponds to the “second wall”. ", The wall 131c corresponds to a" third wall ".

<< Second Embodiment >>
FIG. 10 is a cross-sectional view in which a portion including the intake passage 13 of the intake manifold 100 of the present example is broken, and corresponds to the enlarged view of FIG. In this example, the shape of the EGR pipe 41b is different from that of the first embodiment described above. Since the other configuration is the same as that of the first embodiment described above, the description thereof is incorporated.

  As shown in FIG. 10, the EGR pipe 41 b is a pipe parallel to the intake flow path 13, communicates with the EGR pipe 41 a through the opening 411, and communicates with the EGR pipe 41 c through the opening 412. The opening 411 is disposed on the upstream side of the EGR pipe 41b and opens toward the EGR pipe 41a. The opening 412 is disposed on the downstream side of the EGR pipe 41b and opens toward the cylinder head 200. Yes. The EGR tube 41b is formed so that the area of the cross section in the direction perpendicular to the tube axis is large between the opening 411 and the opening 412. The area of the opening 411 is the area of the opening 412. It is formed to be larger.

  As described above, in this example, the EGR pipe 41 b is formed so as to be parallel to the intake flow path 13. Thereby, the EGR pipe 41b can be manufactured by the same mold as the mold for manufacturing the intake flow path 13. Further, the EGR pipe 41b can be formed by mold casting or injection molding.

  In this example, the area of the opening 411 is formed to be larger than the area of the opening 412. Thereby, the rigidity of the metal mold | die at the time of manufacturing the EGR pipe | tube 41b can be improved. Further, it is possible to prevent the fluid from flowing backward from the intake flow path 13 and flowing into the EGR pipe 41a.

  The EGR pipe 41a of this example corresponds to the “first gas flow path” of the present invention, and the EGR pipe 41b corresponds to the “second gas flow path”.

<< Third Embodiment >>
FIG. 11 is a cross-sectional view of a portion including the intake flow path 13 of the intake manifold 100 of this example, and corresponds to an enlarged view shown in FIG. FIG. 12 is a bottom view of the peripheral portion of the intake passage 3 of the intake manifold 100. This example is different from the above-described first embodiment in that a fluidization variable valve 50 is provided. Since the other configuration is the same as that of the first embodiment described above, the description thereof is incorporated.

  The flow variable valve 50 is a valve for varying the flow in the intake flow path 13, and opens and closes the flow variable valve 50, thereby generating an intake overflow in the combustion chamber of each cylinder, and opening and closing the flow variable valve 50. By adjusting the degree, the degree of intake overflow that occurs in the combustion chamber can be adjusted. The flow variable valve 50 includes a valve body 51 and a rotating shaft 52, and is provided in the intake flow path 13 upstream of the communication port 411 that communicates the EGR pipe 41c and the intake flow path 13. The valve body 51 is formed in a plate shape smaller than the cross-sectional shape of the intake flow path 13, and a notch portion 511 in which a part of the plate shape is cut out is formed in a portion close to the EGR pipe 41 c. ing. The rotating shaft 52 connects the valve body 51 and the inner wall of the intake passage 13. As shown in FIG. 12, when the flow variable valve 50 is closed, the flow rate of the fluid flowing through the intake flow path 13 is the fastest at the portion where the notch 51 is formed, and the EGR pipe 41c communicates. The port 411 is provided toward the portion with the fastest flow velocity in the intake passage 13 in a state where the flow variable valve 50 is closed.

  As described above, in this example, the communication port 411 between the EGR pipe 41c and the intake flow path 13 is provided downstream of the flow variable valve 50, and the flow variable valve 50 is closed in the intake flow path 13 inside. It is provided for the part with the fastest flow velocity. Thereby, EGR gas can be efficiently supplied into the combustion chamber, and the fired product from the EGR gas can be prevented from solidifying and adhering to the flow path.

  In this example, the flow variable valve 50 is provided in the intake flow path 13, but the flow variable valve 50 may be similarly provided in the other intake flow paths 11, 12, and 14-16.

<< 4th Embodiment >>
FIG. 13 is a cross-sectional view in which a portion including the intake flow path 13 of the intake manifold 100 of this example is broken, and corresponds to an enlarged view shown in FIG. In this example, the shape of the wall part 133 and the shape of the cover part 31 differ with respect to 1st Embodiment mentioned above. Since the other configuration is the same as that of the first embodiment described above, the description thereof is incorporated.

  The outer wall of the wall portion 133 a, in other words, the wall surface on the bolt side of the wall portion 133 a is formed to be parallel to the intake flow path 13. The lid portion 31 is provided on the wall portion 133a so as to cover the outer wall of the wall portion 133a. Thereby, the joining surface which joins the cover part 31 and wall part 133a, 133b is formed so that it may become in parallel with the intake flow path 13. FIG.

  As described above, the present example includes the lid portion 31 facing the wall portion 133 a, and the joining surface where the lid portion 31 and the wall portion 133 are joined is formed to be parallel to the intake flow path 13. Thereby, the cover part 31 can be joined to the wall part 133 by vibration welding, and since the cover part 31 can be formed of resin, the weight of the cover part 31 can be reduced. In addition, since the lid portion 31 can be joined to the wall portion 133 in a state parallel to the intake passage 13, the load is applied to the joining surface when performing vibration welding by pressing from the inner wall side of the wall portion 133a. Therefore, the lid portion 31 can be prevented from sliding down from the wall portion 133, and the stability at the time of manufacturing can be enhanced.

  In this example, the above-described configuration may be used not only for the lid portion 31 but also for the lid portion 32.

DESCRIPTION OF SYMBOLS 100 ... Intake manifold 11, 12, 13, 14, 15, 16 ... Intake flow path 111, 121, 131, 141, 151, 161, 180, 171, 172, 180, 181, 182 ... Wall part 131a, 131b, 131c ... Walls 21, 22, 23 ... Flange 21a, 22a, 23a ... Fastening holes 22b, 23b ... Bolts 23c ... Bottom 31, 32 ... Lid 40, 41, 42 ... EGR pipe 40a ... Openings 41a, 41b, 41c ... EGR pipe 411 ... Communication port 50 ... Flow variable valve 51 ... Valve body 511 ... Notch 52 ... Rotating shaft 200 ... Cylinder head 201, 203, 205 ... Intake port 210 ... Fuel injection valve

Claims (7)

Located above the engine body at the center between the banks, a plurality of intake passages are connected in the cylinder row direction for each cylinder, and the left bank intake passage is the cylinder head of the left bank among the plurality of intake passages Of the plurality of intake flow paths, the right bank intake flow path is connected to the right bank cylinder head, and is configured to expand toward the engine body side. In the intake structure of the internal combustion engine including an intake manifold in which a flange is connected to the cylinder head by a bolt provided on the outside,
The intake manifold is
A part of the combustion gas is introduced into the intake flow path, and a gas flow path is provided in the first wall portion on the bolt side among the wall portions of the intake flow path, and is formed by the groove of the flange. ,
The gas flow path is
A first gas flow path parallel to the cylinder row direction;
A second gas flow path communicating with the first gas flow path and parallel to the intake flow path;
A third gas flow path communicating with the second gas flow path and formed by a groove of the flange;
The second gas flow path is
An intake structure for an internal combustion engine, comprising an opening that opens toward the cylinder head . Of the wall portion of the intake flow path, the thickness of the second wall portion that is a part of the gas flow path on the downstream side is the wall portion on the bolt side of the wall portion of the intake flow path. 2. The intake structure of an internal combustion engine according to claim 1, wherein the intake structure is larger than a thickness of the third wall portion that does not form the gas flow path. Prior Symbol second gas flow path,
The area of the opening part opened to the cylinder head side is formed so as to be larger than the area of the opening part on the side communicating with the first gas flow path. Intake structure of an internal combustion engine. The intake flow path has a flow variable valve that varies the flow of fluid in the intake flow path,
A communication port communicating with the gas flow path and the intake flow path,
The downstream of the said flow variable valve and it is provided toward the part with the fastest flow velocity in the said intake flow path in the state which the said flow variable valve closed. An intake structure for an internal combustion engine according to any one of the preceding claims. The gas flow path of the left bank and the gas flow path of the right bank are connected at a central portion between the column of the intake flow channel of the left bank and the column of the intake flow channel of the right bank. The intake structure for an internal combustion engine according to claim 1, wherein the intake structure is an internal combustion engine. Located above the engine body at the center between the banks, a plurality of intake passages are connected in the cylinder row direction for each cylinder, and the left bank intake passage is the cylinder head of the left bank among the plurality of intake passages Of the plurality of intake flow paths, the right bank intake flow path is connected to the right bank cylinder head, and is configured to expand toward the engine body side. In the intake structure of the internal combustion engine including an intake manifold in which a flange is connected to the cylinder head by a bolt provided on the outside,
The intake manifold is
A part of the combustion gas is introduced into the intake flow path, the wall of the intake flow path is provided on the first wall portion on the bolt side, and includes a gas flow path formed by the groove of the flange;
A side surface of a part of the gas flow path is formed by a lid portion facing the first wall portion,
Intake structure for an combustion engine junction you characterized in that parallel to the said intake line joining the other side forming the gas flow path and the lid. The intake structure for an internal combustion engine according to any one of claims 1 to 6, further comprising a fuel injection valve that directly injects fuel into the cylinder from a side in the combustion chamber.

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