JP2004324593A - Air-intake system of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To strengthen tumble in a cylinder 2 without excessively reducing an opening ratio of an intake port 5. <P>SOLUTION: The intake port 5 is formed with a partition wall 11 therein and is divided in a first flow passage 5A on an upper side and a second flow passage 5B on a lower side. An intake control valve 31 is arranged on an upstream side, and a gap 12 serving as a communication passage is formed between the partition wall 11 and a valve body 33. When the intake control valve 31 is put in a closed position, a low pressure area is generated downstream the valve body 33, and intake air is taken from a downstream end of the second flow passage 5B by the pressure difference, flows to the upstream side in the second flow passage 5B and flows back through the gap 12 into the first flow passage 5A. A flow rate passing through a valve clearance on a lower side of an intake valve 7 decreases, a flow rate passing through a valve clearance on the upper side increases, and the tumble is further strengthened. At the same time, a movable guide vane 41 is turned to an operation position and smoothly guides an intake air flow passing through the second flow passage 5B to the gap 12. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an intake device for an internal combustion engine including an intake port connected to a cylinder, and more particularly, to an improvement of an intake device for enhancing gas flow such as tumble and swirl in a cylinder.
[0002]
[Prior art]
For example, in order to achieve stable combustion in a spark ignition type internal combustion engine, gas flow in a cylinder such as a tumble or swirl is very important, and it is necessary to be able to enhance gas flow in a wider operation range.
[0003]
One of the conventionally known methods of enhancing gas flow in a cylinder is to use an intake control valve that blocks a part of a passage cross section of an intake port, as disclosed in Patent Literature 1, to reduce the inside of the intake port. This is a method in which the flowing intake air flow is biased to one side of the intake port. For example, in order to generate a tumble, an intake control valve is disposed below the intake port, and intake air is biased above the intake port, so that the tumble in the cylinder is strengthened.
[0004]
Further, as another method for enhancing the gas flow, as shown in Patent Document 2, a partition wall is provided in the intake port along the longitudinal direction thereof, and one of the flow paths defined by the partition wall is opened and closed. There is known a configuration in which the opening and closing are performed by the opening and closing. For example, in order to generate a tumble, a partition is provided so as to partition the inside of the intake port up and down, and the lower flow path is closed by an on-off valve. As a result, the intake air flows into the cylinder only through the upper flow path, so that the flow velocity and the directivity are higher than those in the above-described example, and the tumble ratio generally improves.
[0005]
[Patent Document 1]
Japanese Patent Application Laid-Open No. 2002-54535
[Patent Document 2]
JP-A-6-159079
[Problems to be solved by the invention]
In any of the known methods as described above, when the gas flow is enhanced, the passage cross-sectional area of the intake port is substantially reduced by an intake control valve or the like. When the ratio of the cross-sectional area is defined as “opening ratio”, generally, the smaller the opening ratio, the higher the gas flow. However, when the opening ratio is reduced, the ventilation resistance increases, and the amount of intake air that can be taken into the cylinder decreases. Therefore, the operating conditions under which the intake control valve and the like can be closed to enhance the gas flow are relatively narrow. It is limited to the range.
[0008]
SUMMARY OF THE INVENTION It is an object of the present invention to provide an intake device for an internal combustion engine that can enhance gas flow in a cylinder without excessively reducing an opening ratio.
[0009]
[Means for Solving the Problems]
The present invention presupposes an intake device for an internal combustion engine in which an intake port is connected to a cylinder of the internal combustion engine and an intake valve opens and closes a downstream end of the intake port. A partition provided along the longitudinal direction of the intake port so as to define the intake port, and an intake control valve that opens and closes one of the flow paths partitioned by the partition. The intake control valve is formed of a plate-shaped valve element that can rotate around a rotation axis, and is located near the upstream end of the partition. When the intake control valve is at a closed position blocking one of the flow paths, a gap is provided between the valve body and the upstream end of the partition.
[0010]
In the present invention, when the intake control valve is in the closed position where one of the flow paths is shielded, the intake air flows to the cylinder side only through the other flow path, and the intake air flows from one side around the intake valve toward the cylinder. A relatively large amount of intake air flows into the cylinder. At the same time, the intake control valve throttles the intake air flow, causing a local pressure drop downstream of the intake control valve, which is caused by the outlet side of the gap that becomes the communication path (the side facing the other flow path). Act on. Therefore, a pressure difference is generated between the downstream end of one of the flow passages shielded by the intake control valve and the gap, and the intake air is sucked from the end and toward the upstream side of the intake port. It flows in the opposite direction and merges into the other flow path through the gap. That is, a part of the intake air returns to the upstream side through the shielded flow path. Therefore, the imbalance in the flow rate or the flow velocity of the intake air flowing around the intake valve is further increased, and the gas flow in the cylinder is effectively enhanced.
[0011]
Further, in the present invention, when the intake control valve is in the closed position as described above, the intake flow that flows backward through one of the blocked flow paths to the upstream side is guided to the gap. A movable guide vane is provided downstream of the intake control valve. The movable guide vane has, for example, a flat plate shape obliquely crossing one of the flow paths, or a plate shape curved so as to smoothly guide the intake air flow to the gap. Therefore, when the intake control valve is in the closed position, the intake flow that flows backward through one of the shielded flow paths to the upstream side is more smoothly guided to the other flow path through the gap.
[0012]
In addition, the term "intake port" in the claims of the present invention does not necessarily mean only a portion inside the cylinder head, and in some embodiments, a part on the upstream side is another member outside the cylinder head, for example, This includes the case where it is configured as part of the intake manifold. For example, an intake control valve may be disposed at a distal end of a passage in an intake manifold branch connected to a cylinder head. In this case, an intake port formed in the cylinder head and a passage in the intake manifold branch may be provided. The range including the leading end portion of the above corresponds to the “intake port” in the claims.
[0013]
【The invention's effect】
ADVANTAGE OF THE INVENTION According to the intake device of the internal combustion engine which concerns on this invention, the gas flow in a cylinder can be improved effectively by recirculating a part of intake air through the flow path shielded by the intake control valve. A stronger gas flow can be obtained without reducing the valve opening ratio. Therefore, an increase in pumping loss due to an increase in ventilation resistance is suppressed, and a large amount of intake air flowing into the cylinder can be secured, so that gas flow can be enhanced in a wide operating range.
[0014]
In particular, in addition to the intake control valve, by providing a movable guide vane for guiding the intake air flowing through one of the shielded flow paths to the gap, the above-described recirculation effect can be more smoothly obtained, and gas such as tumble is provided. The flow can be further enhanced.
[0015]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings.
[0016]
FIG. 1 shows an embodiment in which the present invention is applied to an intake device of a spark ignition type internal combustion engine. This is an example in which a tumble is enhanced particularly as a gas flow. A plurality of cylindrical cylinders 2 are formed in a cylinder block 1, and a pent roof type combustion chamber 4 is formed in a cylinder head 3 that covers the top of the cylinder 2. An intake port 5 and an exhaust port 6 are formed so as to open on the two inclined surfaces of the combustion chamber 4, respectively. An intake valve 7 opens and closes the tip of the intake port 5, and exhausts the tip of the exhaust port 6. Valve 8 opens and closes. Although not shown in detail, the tip end of the intake port 5 is branched in a forked shape, and a pair of intake valves 7 provided in each cylinder open and close the respective tips. Similarly, a pair of exhaust valves 8 are provided for each cylinder. An ignition plug (not shown) is arranged at the center of the combustion chamber 4 surrounded by these four valves. Note that the piston 10 arranged in the cylinder 2 is not a main part of the present invention, and is illustrated as a simple shape having a flat top surface. However, if necessary, a desired shape suitable for combustion using a tumble It may be configured in a shape.
[0017]
As shown in FIG. 1, in the present embodiment, a partition wall 11 is provided along the longitudinal direction of the intake port 5 so as to partition the intake port 5 into two upper and lower regions in a cross section thereof. The partition wall 11 is formed by casting a separate metal plate (for example, a steel plate) when casting the cylinder head 3 with, for example, an aluminum alloy. They are arranged to be close to each other. Here, in the illustrated example, the intake port 5 has a substantially linear shape in the longitudinal direction where the partition wall 11 is present, and is slightly downwardly curved in the downstream portion near the intake valve 7. A partition 11 is also formed in a corresponding shape, extending straight in the upstream part and slightly curving downward in the downstream part.
[0018]
By providing the partition wall 11 as described above, the inside of the intake port 5 except the portion near the intake valve 7 has an upper passage-shaped portion, that is, the first passage 5A, and a lower passage-shaped portion, that is, the second passage-shaped portion. It is divided into a flow path 5B.
[0019]
As will be apparent to those skilled in the art, the terms “upper” and “lower” with respect to the intake port 5 and the intake flow in this specification are based on the upper and lower sides of the cylinder 2 and are absolute It doesn't mean up and down. Further, as described above, the intake port 5 does not necessarily mean only a portion inside the cylinder head 3, and a part on the upstream side is provided with another member outside the cylinder head 3, for example, a part of the intake manifold. It also includes the case where it is configured as a unit.
[0020]
An intake control valve 31 is provided for each cylinder so that the lower second flow path 5B defined by the partition 11 is blocked at the inlet side, that is, at the upstream end. The intake control valve 31 includes a plate-shaped valve element 33 that can rotate around a rotation shaft 32. The rotation shaft 32 is located on an extension of the partition 11 to the upstream side. One end of a plate-shaped valve body 33 is fixed to the rotating shaft 32. Specifically, the valve body 33 has a main valve portion 33a extending to one side from the rotating shaft 32 to open and close the second flow path 5B, and an extension relatively shortly extending to the opposite side. It has a portion 33b. The main valve portion 33a has a shape obtained by bisecting an ellipse according to the cross-sectional shape of the lower side of the intake port 5. On the other hand, the distal end of the extension portion 33b, that is, the downstream end 33c has a linear shape parallel to the edge of the upstream end 11b of the partition wall 11. The rotating shaft 32 is close to the upstream end 11b of the partition 11, but is separated from the upstream end 11b at least so as not to interfere with the extension 33b.
[0021]
The rotating shaft 32 is linked to an actuator (not shown). Under operating conditions for strengthening the tumble, the valve element 33 is controlled to the closed position as shown in the figure, and the lower second flow path 5B is closed. , Shielding at the entrance side. At this time, the main valve portion 33a extends obliquely to the upstream side from the rotary shaft 32, and moves the valve body 33a in a direction to guide the intake air flowing from the upstream side of the intake control valve 31 to the upper first flow path 5A. Is inclined. In other words, the outer shape of the main valve portion 33a is set such that the region below the rotation shaft 32 is completely closed at such a predetermined inclined position. The inclination angle α of the valve body 33 at the above closed position (the angle between the reference line m extending the partition 11 to the upstream side and the valve body 33 is defined as the inclination angle α (see FIG. 2)) is from 90 °. Is also small, for example, in the range of 30 ° to 40 °. Further, when rotated to such a closed position, the downstream extension portion 33b located on the opposite side of the main valve portion 33a is in a state of protruding above the partition wall 11, that is, toward the first flow path 5A. An appropriate size between the upstream end 11b of the partition wall 11 and the downstream end 33c of the extended portion of the valve body 33 is a communication path for communicating the upstream end of the first flow path 5A and the upstream end of the second flow path 5B. A gap 12 is formed. In this embodiment, a gap 12 having a fixed width is secured between the partition wall upstream end 11b and the valve body downstream end 33c, each of which is linear. The width of the gap 12 is, for example, about 1/10 to 1/3 of the equivalent diameter of the intake port 5.
[0022]
On the other hand, under operating conditions where the intake air amount is large, for example, in a high-speed high-load region, as shown in FIG. 3, the intake control valve 31 is controlled to an open position along the longitudinal direction of the intake port 5, and the second flow The road 5B is opened. In this open position, the valve element 33 assumes a posture linearly continuous with the partition wall 11 and is parallel to the intake air flow. Then, the extension 33b is also linearly aligned with the partition 11 so that the tip (downstream end 33c) of the extension 33b is close to the upstream end 11b of the partition 11.
[0023]
A movable guide vane 41 is provided adjacent to the intake control valve 31.
The movable guide vane 41 includes a rotating shaft 42 that is rotated by an actuator (not shown), and a plate-like vane 43 having one end supported by the rotating shaft 42. The rotation shaft 42 is disposed adjacent to the rotation shaft 32 of the intake control valve 31, particularly, adjacent to the downstream side of the rotation shaft 32, and is located substantially on the extension line of the partition 11 together with the rotation shaft 32. ing. In this embodiment, the vane 41 has a flat plate shape and extends downstream from the rotary shaft 32, that is, toward the intake valve 7 in the second flow path 5B.
[0024]
The movable guide vane 41 basically rotates between a non-operation position and an operation position in conjunction with opening and closing of the intake control valve 31. When the intake control valve 31 is at a closed position, 1, when the intake control valve 31 is in the open position, it is controlled to a non-operating position as shown in FIG. In the operating position, the vane 43 extends obliquely downstream from the rotation shaft 42, crosses the second flow path 5B diagonally, and reaches the inner wall surface of the intake port 5 at the tip. At this time, the angle β between the vane 43 and the partition 11 (see FIG. 2) is smaller than 90 °, and desirably ranges from 30 ° to 60 °. On the other hand, in the non-operation position, the vane 43 is in a posture in which the vane 43 overlaps the lower surface of the partition 11 in parallel, and the gap 12 is covered by the vane 43.
[0025]
In addition, the vane 43 is attached to the rotation shaft 42 at a position deviated downward from the center thereof so that the vane 43 can be parallel to each other without interfering with the partition 11 in the non-operation position. Similarly, when the intake control valve 31 is in the open position, the valve body 33 is arranged so that the extension 33b of the valve body 33 can be parallel to the partition wall 11 without interfering with the rotating shaft 42 of the movable guide vane 41. It is mounted at a position offset from the center of the rotation shaft 32 upward. In the illustrated example, the rotating shaft 42 of the movable guide vane 41 is further arranged to be slightly shifted downward from the rotating shaft 32 of the intake control valve 31. For example, the rotating shaft 42 is configured to have a small diameter. And interference with the extension portion 33b can be avoided. As can be understood from FIGS. 1 and 3, the intake control valve 31 and the movable guide vane 41 rotate in opposite directions, respectively, but the rotation shaft 32 and the rotation shaft 42 are coaxially arranged. Is also possible.
[0026]
Next, the operation of the configuration of the above embodiment will be described with reference to FIGS. In these figures, the flow of the intake air is indicated by arrows.
[0027]
In the intake stroke, when the intake valve 7 opens and the piston 10 descends, the intake air flows into the cylinder 2 through a valve gap around the intake valve 7. At this time, if the intake control valve 31 is in the open position and the movable guide vane 41 is in the inoperative position as shown in FIG. 3, the intake air flows through both the first flow path 5A and the second flow path 5B, Since the intake air flows almost uniformly from each part around the valve 7, the gas flow generated in the cylinder 2 is relatively weak.
[0028]
On the other hand, when the intake control valve 31 is controlled to the closed position as shown in FIG. 2, the lower second flow path 5B is blocked, and the intake air flows to the cylinder 2 side only through the upper first flow path 5A. It will flow. In particular, as shown in FIG. 2, the intake air flow is unevenly distributed along the upper inner wall surface 5 a of the intake port 5 (hereinafter, referred to as the upper inner wall surface 5 a), and the lower inner wall surface 5 b (hereinafter, referred to as the lower The flow along the inner side wall surface 5b) is very small. Therefore, when viewed around the intake valve 7, in the valve gap 20 b below the intake valve 7, that is, near the outer periphery of the cylinder 2, the flow rate of the intake air is small, the flow velocity is low, and the upper side of the intake valve 7, In the valve gap 20a on the side close to the center of the cylinder 2, the flow rate of intake air is large and the flow velocity is high. As a result, a tumble (so-called forward tumble) from the intake valve 7 side to the top surface of the piston 10 through the exhaust valve 8 side is generated in the cylinder 2 as shown by an arrow. In the present invention, when the intake control valve 31 is in the closed position as shown in the figure, this portion serves as a throttle, and the intake air is throttled so as to flow only through the first flow passage 5A. In 5A, a local pressure drop occurs near the upstream end 11b of the partition wall 11, and a low pressure region is generated in this portion. Since the gap 12 serving as a communication path between the first flow path 5A and the second flow path 5B has a shape that opens toward the low-pressure region, the gap 12 with the downstream open end 14 of the second flow path 5B is formed. A pressure difference between them. Therefore, the open end 14 serves as an intake air intake port, the intake air is taken in from the open end 14 by the pressure difference, the air flows backward toward the upstream side of the intake port 5, and the first flow path 5 </ b> A To join. That is, after passing through the first flow path 5A, the intake air that is going to expand to the lower area of the intake port 5 is returned to the upstream side through the second flow path 5B and returned to the upper first flow path 5A. Become. Therefore, the amount of intake air flowing through the lower valve clearance 20b of the intake valve 7 is reduced, and at the same time, the amount of intake air flowing through the upper valve clearance 20a is increased, so that a stronger tumble in the cylinder 2 is obtained. In particular, the intake air flow passing through the lower valve gap 20b acts to weaken the tumble in the cylinder 2, but in the above configuration, not only the tumble is strengthened by the flow passing through the upper valve gap 20a, Since the flow through the lower valve gap 20b acting to weaken the tumble is suppressed, the tumble is very effectively strengthened.
[0029]
In particular, in the above embodiment, in the illustrated closed position, the extension 33b of the valve body 33 projects above the partition wall 11, that is, toward the first flow path 5A side, so that the low pressure region is more effectively provided on the back side thereof. Is developed, and the recirculation of the intake air through the gap 12 is reliably performed.
Moreover, in the above embodiment, since the valve element 33 of the intake control valve 31 is inclined as shown in the figure, the intake air flowing along the lower side of the intake port 5 from the upstream side is supplied to the first flow path 5A. I can guide you smoothly.
[0030]
When the intake control valve 31 is in the closed position as described above, the movable guide vane 41 is simultaneously controlled to the operating position as shown in FIG. Therefore, as described above, the intake airflow that flows backward through the lower second flow path 5B is smoothly guided to the gap 12 along the slope of the vane 43, and flows through the upper first flow path 5A. Merges smoothly with the flowing air flow. Therefore, the above-mentioned reflux action can be obtained more strongly, and the tumble can be further strengthened. In particular, even if the valve body 33 of the intake control valve 31 is inclined as described above, the intake flow flowing to the upstream side through the second flow path 5B is guided by the movable guide vanes 41, so that the intake control valve 31 Stagnation and turbulence of the intake air flow on the back side (downstream side) of the valve element 33 can be avoided.
[0031]
Since the second flow path 5B is opened and closed by the upstream intake control valve 31, the vane 43 of the movable guide vane 41 does not necessarily have to reach the lower inner wall surface 5b of the intake port 5; It is only necessary that the length be long enough to guide the flow to the gap 12.
[0032]
The strong tumble formed in the cylinder 2 as described above is very useful for making the air-fuel ratio lean or performing a large amount of exhaust gas recirculation for improving fuel efficiency, and generating a strong tumble in a partial load region. Thereby, stable combustion can be realized under a lean air-fuel mixture or a high exhaust gas recirculation rate, and fuel efficiency can be improved.
[0033]
When the intake control valve 31 is in the open position in a high-speed and high-load region, the movable guide vane 41 is simultaneously in the non-operation position, and the valve body 33 and the vane 43 are linearly connected to the partition 11 as shown in FIG. By arranging, the increase in the intake resistance is avoided, and the gap 12 is covered by the vanes 43, so that the turbulence of the intake flow is suppressed.
[0034]
Although the fuel injection valve is not shown, the intake device having the above configuration is a direct injection type internal combustion engine that directly injects fuel into the cylinder 2, or a port injection type that injects fuel into the intake port 5. It is applicable to any of the internal combustion engines. In the case of a port injection type, it is desirable to arrange a fuel injection valve that injects fuel toward the intake valve 7 on the downstream side as much as possible to avoid interference between the partition wall 11 and the spray.
[0035]
FIG. 4 shows an analysis of the actual flow of intake air in the intake device of the above embodiment, and shows the speed and direction of the flow of each part by minute vectors, that is, arrows. The density of the arrows indicates the flow rate, and a portion where the arrows are densely gathered means that the flow rate is large. However, this shows a flow in a basic configuration without the movable guide vanes 41. FIG. 5 also shows, as a comparative example, the flow of intake air with the gap 12 serving as a communication passage closed. In other words, the configuration in FIG. 5 corresponds to a conventional technique in which the intake flow is unevenly distributed between the partition wall 11 and the intake control valve 31. In both cases, the opening ratio of the intake control valve 31 is the same.
[0036]
As is clear from comparison of these figures, in the comparative example shown in FIG. 5, the intake airflow passing through the upper first flow path 5A is diffused downward and downstream from the downstream end 11a of the partition wall 11. Therefore, there is not a small amount of intake air flowing through the valve gap 20b below the intake valve 7. It should be noted that almost no flow is seen in the second flow path 5B below the partition 11, and the second flow path 5B is in a stagnant state. On the other hand, in FIG. 4 corresponding to the present invention in which the gap 12 is provided, the intake air recirculates from the lower region near the intake valve 7 through the lower second flow path 5B. The intake air flow passing through the valve gap 20b is extremely reduced. Accordingly, the intake air flow passing through the upper valve gap 20a increases. Therefore, the tumble can be effectively strengthened.
[0037]
Next, FIG. 6 shows a different embodiment of the movable guide vane 41. In this embodiment, the plate-shaped vane 43 attached to the rotating shaft 42 is curved from the middle to the tip. Specifically, when in the operating position, the surface facing the downstream side is curved in a direction that becomes concave. Then, the base end of the vane 43 rotates so as to make an angle of about 90 ° with respect to the partition 11, and at this time, the tip end of the vane 43 is connected to the inner wall surface of the intake port 5 (the lower inner wall surface 5 b). To come into contact with
[0038]
Therefore, similarly to the above-described embodiment, when the intake control valve 31 is in the closed position, the intake air flowing through the lower second flow path 5 </ b> B to the upstream side reversely flows to the gap 12 along the curved vane 43. And smoothly merges with the intake air flowing through the upper first flow path 5A. Therefore, the above-mentioned recirculation action can be obtained more strongly, and the tumble can be further strengthened. In the inoperative position of the movable guide vane 41, the vane 43 is at a position indicated by a virtual line.
[0039]
In each of the above embodiments, the intake port 5 is vertically divided by the partition wall 11 to enhance the tumble (longitudinal vortex). However, by setting the direction in which the partition wall 11 is arranged appropriately, the swirl ( It is also possible to enhance the lateral vortex and the swirling flow in the direction in which swirl and tumble are combined.
[Brief description of the drawings]
FIG. 1 is a sectional view showing an embodiment of an intake device according to the present invention.
FIG. 2 is an explanatory diagram when the intake control valve is at a closed position.
FIG. 3 is an explanatory diagram when the intake control valve is at an open position.
FIG. 4 is an explanatory diagram showing a flow of intake air in a basic configuration of the intake device.
FIG. 5 is an explanatory diagram showing a flow of intake air in an intake device of a comparative example.
FIG. 6 is a sectional view showing a different embodiment of the movable guide vane.
[Explanation of symbols]
5 intake port 7 intake valve 11 partition 12 gap 31 intake control valve 41 movable guide vane

Claims (9)

In an intake device of an internal combustion engine, an intake port is connected to a cylinder of the internal combustion engine, and an intake valve opens and closes a downstream end of the intake port.
A partition wall provided along the longitudinal direction of the intake port so as to partition the intake port into two regions in its cross section;
An intake control valve comprising a rotatable plate-shaped valve element located close to the upstream end of the partition, and opening and closing one flow path defined by the partition.
When the intake control valve is in the closed position blocking one flow path, a gap is provided between the upstream end of the partition and the valve element, and from this flow path from one flow path to the other flow path through this gap. The intake air is configured to return,
An intake device for an internal combustion engine, comprising: a movable guide vane downstream of the intake control valve so as to guide an intake air flowing backward through one of the blocked flow paths to the upstream side into the gap. The movable guide vane has a flat plate shape, and is located at a position inclined with respect to the partition wall so as to obliquely cross the one flow path when the intake control valve is at a closed position. An intake device for an internal combustion engine according to claim 1. The movable guide vane has a plate shape positioned so as to cross the one flow path when the intake control valve is in the closed position, and controls the intake flow that flows backward in the one flow path to the upstream side. 2. The intake device for an internal combustion engine according to claim 1, wherein the intake device is curved so as to be guided toward the gap. The intake device for an internal combustion engine according to any one of claims 1 to 3, wherein the movable guide vane rotates about a rotation shaft located upstream of the gap. The rotation axis of the intake control valve is located on an extension of the partition, and the rotation axis of the guide vane is coaxial with or adjacent to the rotation axis of the intake control valve. An intake device for an internal combustion engine according to claim 1. 6. The movable guide vane is located at a position overlapping with the partition wall so as to cover the gap when the intake control valve opens one flow path. An intake device for an internal combustion engine. 7. The intake device for an internal combustion engine according to claim 1, wherein when the intake control valve is at a closed position, a part of the valve body projects toward the other flow path. The internal combustion engine according to any one of claims 1 to 7, wherein when the intake control valve is at a closed position, the valve body is inclined in a direction to guide the intake air flow to the other flow path. Engine intake device. 9. The air conditioner according to claim 1, wherein the partition wall is provided so as to partition an intake port up and down with respect to a vertical direction of the cylinder, and a lower flow path is blocked by the intake control valve. 10. An intake device for an internal combustion engine according to any one of the above.

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