JP2012219765A - Air-intake apparatus of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve mountability by reducing a physical size of the entire intake vortex generating device for generating tumble flows in a combustion chamber of an internal combustion engine.SOLUTION: A supporter 1 and a casing 2 include first and second welding ribs 41, 42, respectively, which are mutually abut to be welded with vibration. An inside burr sump for accumulating weld burrs generated during vibration welding with the first welding rib 41 and the second welding rib 42 is provided inside of the first and second welding ribs 41, 42. A flange 33 of a housing 3 is clamped and held between the weld burrs 61 invaded and cured in the inside burr sump and a step 72 of the flange 32 of the casing 2. Thus, there is no need for providing an extra amplitude clearance between an end surface part of the housing 3, an intake air outlet port of an intake air passage 12, and a curved surface part of a rotary valve at the vibration welding operation of the first and second welding ribs 41, 42.

Description

  The present invention relates to an intake device for an internal combustion engine having an intake duct that forms an intake passage through which intake air drawn into the internal combustion engine flows, and in particular, an internal combustion engine having an intake control valve that controls intake air flowing through the intake passage of the internal combustion engine. It relates to the intake system of the engine.

[Conventional technology]
Conventionally, as an intake device for an internal combustion engine, as shown in FIG. 7, an intake manifold that forms an intake passage for supplying intake air to a combustion chamber of the internal combustion engine (engine), and an intake manifold that can be opened and closed are accommodated. A U-shaped rotary valve 101, and a shaft 102 extending in the direction of the rotation axis of the rotary valve 101, and the intake air flowing through the intake passage is biased to the upper portions of the intake passage and the intake port so that the combustion chamber of the engine An intake device (valve unit) for an internal combustion engine provided with a tumble control valve that generates a swirling flow in the vertical direction is known (for example, see Patent Document 1).
The intake manifold is configured by first and second divided bodies that are divided into at least two. These first and second divided bodies are all integrally formed of synthetic resin.

A 1st division body is the cylindrical casing 103 which accommodates the rotary valve 101 inside so that opening and closing is possible, and supports the shaft 102 rotatably.
The second divided body is a cylindrical duct 104 accommodated in the internal space of the casing 103. An intake passage 105 through which intake air sucked into the combustion chamber of the engine flows is formed inside the duct 104. In addition, an intake passage 106 provided downstream of the intake outlet portion of the intake passage 105 is formed in the casing 103.
First and second flanges 107 and 108 facing each other are provided at upstream ends of the casing 103 and the duct 104.
The first and second flanges 107 and 108 are provided with annular first and second welding ribs 111 and 112 which are brought into contact with each other and vibration welded.
On both sides of the first and second welding ribs 111 and 112, annular first and second concave grooves for accommodating welding burrs generated during vibration welding are formed, respectively.

The rotary valve 101 rotates with a curve having a predetermined radius of curvature around the rotation axis of the shaft 102 so as to follow the outlet end face (partial cylindrical curved surface portion 121) of the duct 104 and the intake outlet portion of the intake passage 105. It has a curved surface portion 115 having a circular arc cross section that reciprocates on the operating line. The curved surface portion 115 is opposed to the curved surface portion 121 of the duct 104 and the intake outlet portion of the intake passage 105 with a clearance (clearance) S therebetween when the rotary valve 101 is fully closed.
Here, in order to further strengthen the swirl flow (especially tumble flow) in the combustion chamber of the engine, the lower side of the intake passage 105 is closed, and the intake flow is biased toward the central portion in the width direction on the upper side of the intake passage 105. There is a need. For this reason, an opening 116 through which intake air can pass even if the rotary valve 101 is fully closed is formed in the upper center of the curved surface portion 115 of the rotary valve 101.

[Conventional technical problems]
However, in the valve unit described in Patent Document 1, the second flange 108 welded and fixed to the first flange 107 and the duct 104 accommodated in the casing 103 are integrated by a synthetic resin.
As described above, when the second flange 108 and the duct 104 are integrated, it is necessary for the vibration welding operation between the curved surface portion 115 of the rotary valve 101 and the curved surface portion 121 of the duct 104 and the intake outlet portion of the intake passage 105. Amplitude clearance (α) is required.
Accordingly, it is necessary to enlarge (S + α) the gap (S) between the curved surface portion 115 of the rotary valve 101 and the curved surface portion 121 of the duct 104 and the intake outlet portion of the intake passage 105 by the amplitude clearance (α). It is necessary to enlarge the physique. Therefore, as the overall size of the product increases, it becomes a factor that deteriorates the mountability of the valve unit.

Further, when the first and second welding ribs 111 and 112 are vibration-welded, the welding surfaces of the first and second welding ribs 111 and 112 are inclined, or the welding margin of the first and second welding ribs 111 and 112 is used. May vary from product to product, resulting in weld misalignment. When the gap S between the curved surface portion 115 of the rotary valve 101 and the curved surface portion 121 of the duct 104 and the intake outlet portion of the intake passage 105 cannot be controlled uniformly as a cause of welding deviation for each product, the curved surface portion of the rotary valve 101 There is a possibility that the gap S between 115 and the curved surface portion 121 of the duct 104 and the intake outlet portion of the intake passage 105 may be further increased.
In addition, since the clearance S between the curved surface portion 115 of the rotary valve 101 and the curved surface portion 121 of the duct 104 and the intake outlet portion of the intake passage 105 is widened, the intake flow flowing through the intake passage 105 is on both sides of the curved surface portion 115 in the width direction. When the rotary valve 101 is fully closed, a strong intake flow cannot be generated at the upper center of the intake passage 105.
Therefore, the swirl flow (especially tumble flow) in the combustion chamber of the engine cannot be further strengthened, and there is a problem that improvement in combustion efficiency and improvement in fuel efficiency due to stabilization of combustion cannot be expected.

JP 2009-092280 A

  An object of the present invention is to provide an intake device for an internal combustion engine that can reduce the size of the entire product and improve the mountability.

The invention according to claim 1 (intake device of an internal combustion engine) includes a synthetic resin intake duct surrounding the periphery of an intake passage through which intake air sucked into the internal combustion engine flows.
The intake duct is configured by first to third divided bodies that are divided into at least three.
The first and second divided bodies protrude from the first and second opposed portions so as to face each other, and the first and second opposed portions are arranged to face each other with a predetermined distance (space) therebetween, and First and second welding ribs that are welded to face each other are provided.
The first facing portion of the first divided body has a burr pool for accommodating a welding burr generated at the time of welding the first welding rib and the second welding rib between the second facing portion of the second divided body. Provided.
The third divided body is a fitting part (first engaging part) that has entered and hardened into the burr pool and is fitted between the second facing part (second engaging part) of the second divided body ( Locked portions, for example, flanges, maximum outer diameter portions, fitting convex portions, etc.) are provided.

According to invention of Claim 1, it generate | occur | produces at the time of the welding of a 1st welding rib and a 2nd welding rib, and between the 1st opposing part of a 1st division body, and the 2nd opposing part of a 2nd division body. The fitting portion of the third divided body between the welded burr (first locking portion) that has entered and hardened into the formed burr pool and the second opposing portion (second locking portion) of the second divided body. (Locked portion) is sandwiched and held.
Thus, during the welding process in which the first welding rib protruding from the first facing portion of the first divided body and the second welding rib protruding from the second facing portion of the second divided body are brought into contact with each other and welded, It is not necessary to provide the necessary amplitude clearance. Thereby, since the physique of the whole product can be reduced in size, the mounting property of the apparatus with respect to a vehicle can be improved, for example. Moreover, the 1st-3rd division body divided | segmented into at least 3 can be fixed cheaply.
The burr pool is a concave groove provided adjacent to the first and second welding ribs (for example, adjacent to the inner side (intake passage side)).

According to the second aspect of the present invention, the locking portion (second locking) for locking the fitting portion of the third divided body (in a state of being in direct contact) with the second facing portion of the second divided body. Part).
In addition, you may provide the side wall (step) which opposes the welding burr | flash which entered the burr | flash pool and hardened | cured as a 2nd locking part. In this case, the stepped portion of the locking portion directly contacts the third divided body and restricts the position of the third divided body in the intake flow direction, whereby the intake air of the third divided body with respect to the first and second divided bodies. Positioning in the flow direction is performed.
Moreover, you may provide the surrounding wall which surrounds the circumference | surroundings of the 3rd division body in the circumferential direction as a 2nd latching | locking part. In this case, the peripheral wall of the second locking portion directly contacts the third divided body and restricts the position of the third divided body in the direction substantially orthogonal to the intake flow direction, thereby the first and second divided portions. The body is positioned in a direction substantially perpendicular to the intake flow direction of the third divided body.

The first welding rib and the second welding rib are brought into contact with each other, and the second welding rib is moved relative to the first welding rib fixed by the jig so that the tip of the first welding rib and the second welding rib are moved. When vibration welding the tip of the rib, the width of the welding surface of the first welding rib may be wider than the width of the welding surface of the second welding rib. This facilitates the vibration welding operation. Moreover, the volume (volume) of the welding burr | flash which generate | occur | produces at the time of vibration welding can be reduced compared with the type whose width of the welding surface of a 1st, 2nd welding rib is the same dimension.
Further, the first welding rib and the second welding rib are brought into contact with each other, and the first welding rib is moved relative to the second welding rib fixed by the jig, so that the tip of the first welding rib and the second welding rib are moved. When vibration welding the tip of the rib, the width of the welding surface of the first welding rib may be narrower than the width of the welding surface of the second welding rib. This facilitates the vibration welding operation. Moreover, the volume (volume) of the welding burr | flash which generate | occur | produces at the time of vibration welding can be reduced compared with the type whose width of the welding surface of a 1st, 2nd welding rib is the same dimension.

According to invention of Claim 3, the 3rd division body has provided the 3rd opposing part arrange | positioned facing a predetermined distance between the 1st opposing parts of the 1st division body. . Further, the first divided body protrudes toward the third opposed portion side of the third divided body from the first opposed portion located on the intake passage side (inner side) with respect to the first and second weld ribs. Is provided. The tips of the ribs are in direct contact with the third facing portion of the third divided body.
Thereby, the 3rd opposing part of the 3rd division object is inserted and held between the rib rib of the 1st division object, and the 2nd opposing part (and the 2nd locking part) of the 2nd division object. . Thereby, the 3rd counter part of the 3rd division object can be fixed more certainly to the 1st counter part of the 1st division object, and the 2nd counter part of the 2nd division object.

According to invention of Claim 4, the 3rd division body has provided the 3rd opposing part arrange | positioned facing a predetermined distance between the 1st opposing parts of the 1st division body. . Further, the third divided body is a ridge rib that protrudes from the third facing portion located closer to the intake passage side (inner side) than the first and second welding ribs toward the first facing portion side of the first divided body. Is provided. The tips of the ribs are in direct contact with the first facing portion of the first divided body.
Thereby, the 3rd opposing part and protrusion rib of a 3rd division body are pinched | interposed between the 1st opposing part of a 1st division body, and the 2nd opposing part (and 2nd latching | locking part) of a 2nd division body. Held. Thereby, the 3rd counter part of the 3rd division object can be fixed more certainly to the 1st counter part of the 1st division object, and the 2nd counter part of the 2nd division object.

According to invention of Claim 5, the 3rd division body has provided the 3rd opposing part arrange | positioned facing a predetermined distance between the 1st opposing parts of the 1st division body. . Moreover, the 3rd division body is provided with the 3rd welding rib which protrudes so that it may face a 1st welding rib from a 3rd opposing part, and is abutted and welded to a 1st welding rib with a 2nd welding rib.
Thereby, since the 1st-3rd division body divided | segmented into at least 3 can be weld-joined simultaneously, the 1st opposing part of a 1st division body and the 2nd opposing part of a 2nd division body WHEREIN: It is possible to more reliably fix the three facing portions.

According to the sixth aspect of the present invention, there is provided a synthetic resin intake duct surrounding the intake passage through which intake air sucked into the internal combustion engine flows, and an intake control valve for controlling the intake air flowing through the intake passage by an opening / closing operation. ing.
A tumble control valve (swirl control valve) that generates a swirling flow in the combustion chamber for each cylinder of the engine may be employed as the intake control valve.
According to the seventh aspect of the present invention, the intake control valve is centered on a rotation axis extending in a direction perpendicular to the intake flow direction in the intake duct and a center point located on the central axis of the rotation axis. The rotary valve etc. which reciprocately move on the rotation action line which is the curve of the curvature radius which were made.

According to invention of Claim 8, the 3rd division body has the cylindrical duct main body which forms an intake passage.
According to the invention described in claim 9, the second divided body has a bearing portion that supports (rotatably) the rotation shaft of the intake control valve.
According to the invention described in claim 10, the intake passage has the outlet portion opened at the downstream end surface of the duct body in the intake flow direction. In addition, the rotary valve includes a facing portion that faces the exit portion of the duct body with a gap when fully closed.

According to invention of Claim 1, 2, and Claims 6-10, since the welding shift | offset | difference for every product can be prevented, the state which positioned the housing of the 3rd division body with respect to the 2nd division body which has a bearing part It can be fixed with. As a result, the gap between the rotary valve of the intake control valve and the downstream end face of the housing of the third divided body and the outlet portion of the intake passage does not vary from product to product. The gap can be made uniform.
Therefore, when the intake control valve is used as an intake control valve (such as a tumble control valve or a swirl control valve) that adjusts the swirling flow generated in the combustion chamber of the internal combustion engine by an opening / closing operation, the swirling flow in the combustion chamber of the internal combustion engine is reduced. Further strengthening can be achieved. As a result, it is possible to improve combustion efficiency and fuel consumption by stabilizing combustion.

(Example 1) which was the front view which showed the generation | occurrence | production range of the welding burr | flash which got into the inner side burr | flash pool and was hardened. (Example 1) which is sectional drawing which showed the fully-closed state of the tumble control valve. (Example 1) which is sectional drawing which showed the fully open state of the tumble control valve. (A), (b) is sectional drawing which showed the housing vibration welding fixation structure with respect to a casing (Example 1 and 2). (A), (b) is sectional drawing which showed the housing vibration welding fixation structure with respect to a casing (Example 3 and 4). (Example 5) which was the front view which showed the generation | occurrence | production range of the welding burr | flash which entered and hardened | cured the inner burr | flash pool. (A) is sectional drawing which showed the fully-closed state of the tumble control valve, (b) is sectional drawing which showed the fully-open state of the tumble control valve (prior art).

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
The object of the present invention is to improve the mountability by reducing the size of the entire product, and to prevent the welding displacement for each product. Between the welded burr (first locking portion) and the second locking portion (step difference, etc.) of the second divided body. Realized by being sandwiched and held.

[Configuration of Example 1]
FIGS. 1 to 4 show Embodiment 1 of the present invention. FIG. 1 is a view showing the generation range of weld burrs that have entered the inner burr pool and hardened, and FIG. 2 is a fully closed state of the tumble control valve. FIG. 3 is a diagram showing a fully opened state of the tumble control valve.

  An intake device for an internal combustion engine of this embodiment includes an electronic throttle device that controls the flow rate of intake air sucked into a combustion chamber and an intake port of the internal combustion engine (engine) by an opening / closing operation, and an intake passage downstream of the electronic throttle device. And the intake air flowing through the intake port drifts to the upper part (or center of the upper part) of the intake passage and intake port to generate a vertical swirl flow (intake vortex flow: hereinafter referred to as tumble flow) in the combustion chamber of each cylinder An intake eddy current generating device.

Here, as the engine, a multi-cylinder gasoline engine having a plurality of cylinders that generate output by heat energy obtained by burning a mixture of intake air and fuel in a combustion chamber is employed. However, it is not limited to a multi-cylinder gasoline engine, and a multi-cylinder diesel engine may be applied.
In the engine, a plurality of cylinders (cylinder bores) and a plurality of combustion chambers are arranged in series in the cylinder arrangement direction.
An engine body (cylinder head, cylinder block, etc.) is formed with an intake port that is opened and closed by an intake valve and an exhaust port that is opened and closed by an exhaust valve.

A spark plug is attached to the cylinder head of the engine so that the tip end portion is exposed in the combustion chamber of each cylinder. The cylinder head is provided with an injector (electromagnetic fuel injection valve) that injects fuel into each intake port at an optimal timing.
A piston connected to the crankshaft is supported in each cylinder bore via a connecting rod so as to be slidable in the reciprocating sliding direction.
An intake pipe, in which an intake passage is formed, is connected to a plurality of intake ports that are independently connected to the combustion chamber of each cylinder. Further, an exhaust pipe having an exhaust passage formed therein is connected to a plurality of exhaust ports that are independently connected to the combustion chamber of each cylinder.

The engine is equipped with an air cleaner, an electronic throttle device, an intake vortex generator, and the like.
The air cleaner has a filter element (filtering element) for filtering outside air (intake air) introduced into the air introduction passage from an outside air introduction port opened at the upstream end of the inlet duct (outside air introduction duct).
The outlet end of the air cleaner is connected to the throttle body of the electronic throttle device via an intake duct (rubber hose) that forms an intake passage through which intake air that has passed through the air cleaner flows. The outlet end of the throttle body communicates with the intake duct via the upstream end portion of the intake manifold. The outlet end of the upstream end portion of the intake manifold communicates with the combustion chamber and the intake port for each cylinder of the engine via an intake duct.

  The electronic throttle device includes a throttle body connected to an outlet end of an air cleaner, a throttle valve housed in the throttle body so as to be openable and closable, a shaft for supporting and fixing the throttle valve, and a rotary drive for driving the shaft. An actuator that opens and closes the valve, and a throttle opening sensor that detects the rotation angle (throttle opening) of the shaft of the throttle valve, and each engine is controlled according to the throttle opening corresponding to the valve opening of the throttle valve. This is a system (intake control device for an internal combustion engine) that variably controls the flow rate of air sucked into a combustion chamber for each cylinder.

  An intake vortex generator is installed in an engine room of a vehicle such as an automobile together with an electronic throttle device, and an intake duct made of a synthetic resin from which intake air flows from the throttle body or surge tank via the upstream end of the intake manifold ( An intake manifold on the downstream side of the intake manifold) and an intake control valve (tumble control valve) that adjusts the tumble flow generated in the combustion chamber of each cylinder of the engine by opening and closing operation, and in the combustion chamber of each cylinder of the engine This is a system (intake control device for an internal combustion engine) that generates a vertical swirl flow (intake vortex flow: hereinafter referred to as tumble flow).

Here, the intake duct is constituted by first to third divided bodies divided into at least three. These first to third divided bodies are all integrally formed of a synthetic resin such as a thermoplastic resin (for example, polyamide resin: PA).
The first divided body is a vibration welding member (supporter) 1 that is vibration welded to at least the second divided body. The second divided body is the casing 2 that is installed so as to surround the third divided body. The third divided body is a housing (duct body) 3 provided in a plurality (for the number of cylinders) for one casing 2.
Details of the supporter 1, the casing 2, and the housing 3 will be described later.

The tumble control valve includes a plurality of rotary valves housed in the casing 2 so as to be openable / closable (rotatable), a metal pin rod (rotary shaft) 4 extending in the rotational axis direction of the rotary valves, and the pin rod 4. The molded product (shaft) 5 made of synthetic resin molded so as to partially cover the periphery of the motor, and a motor as a power source, and the opening (rotation angle) of a plurality of rotary valves are collectively changed Actuator.
The actuator is attached to the outer wall of the casing 2. This actuator has a motor that generates a driving force (torque) that receives a supply of electric power to drive a plurality of rotary valves, and a speed reduction mechanism that decelerates the rotation of the motor and transmits it to the pin rod 4. A motor for driving a plurality of rotary valves is electrically connected to a battery mounted on a vehicle such as an automobile via a motor drive circuit electronically controlled by an engine control unit (electronic control unit: hereinafter referred to as ECU). ing.

The plurality of rotary valves are housed in the inner space of the casing 2 so as to be rotatable (swingable), and are curved with a predetermined radius of curvature (circular arc) around the center point located on the rotation center axis of the pin rod 4. This is a swing-type tumble control valve that adjusts the tumble flow generated in the combustion chamber of each cylinder of the engine by reciprocating (opening and closing operation) on a rotation operating line that is a curve).
The plurality of rotary valves constitute a valve body of the tumble control valve, and are arranged in parallel in the casing 2 at a predetermined interval in the rotation axis direction of the pin rod 4.
The plurality of rotary valves are fully opened using the torque of the actuator, particularly the motor. The plurality of rotary valves are fully closed using the torque of the actuator, particularly the motor. That is, the rotation angle of the plurality of rotary valves is changed in the full movable range from the fully open position to the fully closed position using the torque of the motor.

  The plurality of rotary valves are integrally formed in a predetermined shape with a metal material. These rotary valves include a pair of side plates 7 having a pair of coupling portions 6 coupled to the pin rod 4 via the molded body 5, and opposite end portions of the side plates 7 with respect to each coupling portion side. A U-shaped valve plate (valve body) 8 is provided to connect the two. When the plurality of rotary valves are fully opened, the intake passages 11 to 13 formed in the casing 2 are opened and stored in a valve storage recess 14 formed in the lower part of the internal space of the casing 2, particularly in the lower part of the housing 3. Storage posture (storage state).

The two coupling portions 6 are metal ring plates surrounding the pin rod 4 and the molded body 5, and are supported and fixed to each valve holding portion of the molded body 5 by insert molding. Each coupling portion 6 is formed with a fitting hole into which the molded body 5 is fitted. The two coupling portions 6 are integrally formed on the pin rod side of the pair of side plates 7.
The pair of side plates 7 extend straight from the two coupling portions 6 toward the radially outer side (free end portion side, front end side) of the pin rod 4. These side plates 7 are formed by bending both ends of the valve plate 8 in the rotational axis direction (axial direction parallel to the pin rod 4) to the pin rod side (coupling portion side) at substantially right angles.

The pair of side plates 7 have outer surfaces that are arranged to face each other with a predetermined gap (side clearance) between the inner surfaces of the left and right wall portions of the casing 2. Further, the pair of side plates 7 have inner side surfaces that are arranged to face each other with a predetermined gap (side clearance) between the outer side surfaces of the left and right wall portions of the housing 3.
The valve plate 8 is a connecting portion that connects the free ends of the pair of side plates 7 (ends opposite to the pin rod side). The valve plate 8 reciprocates in the rotational direction around the center point located on the rotational center axis of the pin rod 4 so that the outer side of the housing 3 is along the downstream end surface of the left and right wall portions of the housing 3. The opening area of the intake passages 11 to 13 is changed.

The valve plate 8 is provided with a partially cylindrical curved surface portion (opposing portion) 15 having a predetermined radius of curvature centering on a center point located on the rotation center axis of the pin rod 4.
Further, the valve plate 8 causes the intake air flowing through the intake passages 11 and 12 when the rotary valve is fully closed to drift to one side (upper wall portion side of the housing 3) of the intake passage 12 in the vertical (height) direction. An opening (notch) 16 for generating a tumble flow in the combustion chamber is formed.
The opening 16 opens near the flow path wall on one side (upper wall side) in the vertical direction of the housing 3 when the rotary valve is fully closed.
The opening 16 may be opened at the upper center in the width direction of the intake passage 12. Further, the tumble flow generated in the combustion chamber can be strengthened as the opening area of the opening 16 is reduced.

The pin rod 4 is a rotating shaft extending in a direction orthogonal to the intake flow direction in the intake passages 11 to 13 of the casing 2, and is arranged in a direction in which the plurality of intake passages 11 to 13 are arranged (relative to the cylinder arrangement direction of the engine). It is arranged so as to extend straight in the direction of the rotation axis parallel to the (parallel direction).
The pin rod 4 is a polygonal cross section shaft whose cross section perpendicular to the rotation axis direction is formed in a polygonal shape (for example, a quadrangular shape), and is integrally formed of a metal material.
One end portion of the pin rod 4 in the rotation axis direction protrudes from one end surface of the casing 2 to the outside and is connected to the actuator. Further, the other end portion of the pin rod 4 in the rotation axis direction protrudes to the outside from the other end surface of the molded body 5 and is rotatably supported by a bearing press-fitted and fixed to the casing 2. In addition, the other end part of the rotating shaft direction of the pin rod 4 is cut so that a cross section may become circular shape.

The pin rod 4 connects a plurality of rotary valves via the molded body 5 so as to be interlocked. Thereby, the opening degree of a plurality of rotary valves can be changed at once by one pin rod 4.
The molded body 5 is a cylindrical resin member (synthetic resin-made resin molded portion) that is installed corresponding to each of the plurality of rotary valves and is formed so as to surround the pin rod 4 in the circumferential direction. The molded body 5 has a valve holding part that couples (supports and fixes) a plurality of rotary valves.

  Next, details of the casing 2 and the housing 3 of this embodiment will be described with reference to FIGS. 1 to 4B. Here, FIG. 4B is a diagram showing a housing vibration welding and fixing structure for the casing.

The upstream end portion of the intake manifold includes a surge tank that reduces the pressure pulsation of intake air and a plurality of intake branch pipes that are respectively connected to a plurality of outlets of the surge tank.
The surge tank consists of a surge tank body that distributes intake air to a plurality of intake branch pipes connected to the combustion chamber and intake port of each cylinder of the engine, and an intake intake pipe that introduces intake air from the throttle body to the surge tank body (throttle connection) Tube).
The downstream end of the intake manifold is constituted by a divided supporter 1, casing 2, and housing 3.

In the casing 2, a plurality of intake passages 12 and 13 are formed, which are connected to the outlet ends of the plurality of intake branch pipes via the intake passage 11, respectively. That is, the casing 2 is installed so as to surround the intake passages 12 and 13 in the circumferential direction.
The intake passages 11 to 13 constitute independent intake passages (blowing passages) for blowing the intake air flowing out from the upstream end of the intake manifold to the intake ports of the respective cylinders of the engine.
The plurality of intake passages 11 to 13 are independently connected to the combustion chamber for each cylinder of the engine via each intake port of the cylinder head.

The casing 2 is integrally formed of a synthetic resin, and has a coupling flange 17 that is fastened and fixed to a coupling end surface (fastening surface) of a cylinder head of the engine using a fastening bolt.
The casing 2 includes a plurality of outer ducts 21 extending in the axial direction (intake air flow direction) of the intake passages 12 and 13 and a connecting portion 22 that connects the two adjacent outer ducts 21.
The plurality of outer ducts 21 are partition bodies that surround the housing 3 and the intake passages 12 and 13 in a U-shape, and are opposed to each other with a space (hollow part) parallel to the rotation axis direction of the pin rod 4. Left and right wall portions and upper and lower wall portions connecting these left and right wall portions.
The upper wall portion of the casing 2 is provided with a U-shaped storage recess (bearing portion) 23 that opens toward the radially outer side of the pin rod 4 and extends from the opening side to the back side. These housing recesses 23 have axial holes (bearing holes) extending in the rotation axis direction (thrust direction) parallel to the pin rod 4. On the back side of the plurality of storage recesses 23, a bottom portion that closes the back side of the storage recesses 23 is provided. An arc-shaped concave curved surface having a predetermined radius of curvature around the rotation axis of the pin rod 4 is formed at the bottom of the plurality of storage recesses 23.

The plurality of housings 3 are configured separately from the casing 2. The housing 3 is a rectangular tube-shaped duct body (peripheral wall portion) that is installed so as to surround the intake passage 12 in the circumferential direction and extends in the duct circumferential direction. The housing 3 is inserted and held in the internal space of the casing 2.
The housing 3 has left and right wall portions facing each other with an axial gap (hollow portion) parallel to the rotation axis direction of the pin rod 4 and upper and lower wall portions connecting (connecting) these left and right wall portions.
The intake passage 12 constitutes an independent intake passage (relay passage) that guides the intake air flowing from the intake passage 11 of the supporter 1 to the intake passage 13. The intake passage 12 has an intake inlet portion that opens at the upstream end face of the housing 3 in the intake flow direction, and an intake outlet portion that opens at the downstream end face of the housing 3 in the intake flow direction.

On the downstream end surfaces of the left and right wall portions of the housing 3, an end surface portion 24 having a concave curved surface shape is provided. The end surface portion 24 has a radius of curvature smaller than the radius of curvature of the curved surface portion 15 by a clearance (clearance). Thus, the curved surface portion 15 of the valve plate 8 is disposed to face the end surface portion 24 of the housing 3 and the intake outlet portion of the intake passage 12 with a clearance (clearance) when the rotary valve is fully closed. .
At the downstream end portion of the upper wall portion of the housing 3, a hook-shaped projection 25 is formed so as to protrude from the downstream end surface of the housing 3 toward the downstream side in the intake flow direction. The protrusion 25 forms an opening 16 with the upper end surface (notch) of the valve plate 8 when the rotary valve is fully closed.

[Features of Example 1]
The supporter 1, the casing 2, and the housing 3 are integrally formed of a heat-resistant synthetic resin material (for example, a thermoplastic resin such as polyamide resin (PA)).
First and second opposing portions (flanges 31 and 32) that are arranged to face each other with a predetermined distance (space such as a burr pool) are integrally formed at the upstream end portions of the supporter 1 and the casing 2, respectively. Is provided. The flange 32 is arranged so as to surround the periphery of the upstream end portion of the housing 3 in the circumferential direction.

A third facing portion (flange 33) is disposed integrally with the upstream end portion of the housing 3 so as to be opposed to the flange 31 of the supporter 1 with a predetermined distance (space such as a burr pool). Is provided. The outer peripheral end of the flange 33 is sandwiched and held between the welding burr 61 that has entered and hardened into the inner burr pool and the second locking portion (steps 71 and 72) of the flange 32 of the casing 2. A fitting part (locked part) is formed.
A plurality of flanges 31 to 33 are provided (for the number of cylinders). Further, the plurality of flanges 31 are connected to each other through two connecting portions 34. That is, the connecting portion 34 connects the two adjacent flanges 31.

The flange 31 of the supporter 1 has a facing surface that faces a facing surface of the flange 32 of the casing 2 and a facing surface of each flange 33 of the housing 3.
The supporter 1 and the casing 2 are provided with first and second welding ribs 41 and 42 which protrude from the flanges 31 and 32 so as to face each other and are brought into contact with each other and subjected to vibration welding. These first and second welding ribs 41 and 42 are provided so as to surround a periphery of an inner burr pool described later.

The plurality of first welding ribs 41 protrude from the intermediate portion in the protruding direction of each flange 31 toward the flange side of the casing 2. These first welding ribs 41 are angular annular (or partial annular) protruding ribs.
The plurality of second welding ribs 42 protrude from the intermediate portion in the protruding direction of each flange 32 toward the flange side of the supporter 1. These second welding ribs 42 are angular (or partially annular) protruding ribs.

The first and second welding ribs 41 and 42 are provided so as to entirely or partially surround the periphery of the intake inlet portion of the intake passage 12 opened at the inlet end surface of the casing 2.
Further, the width of the welding surface of the first welding rib 41 is made narrower than the width of the welding surface of the second welding rib 42. That is, the width of the welding surface of the second welding rib 42 is made wider than the width of the welding surface of the first welding rib 41.
As a result, the first welding rib 41 of the supporter 1 is reciprocated in the width direction of the second welding rib 42 with respect to the second welding rib 42 of the casing 2 to vibrate the first and second welding ribs 41, 42. In this case, the first and second welding ribs 41 and 42 can be welded and joined efficiently. Further, the amount of welding burrs generated during vibration welding can be reduced.

On both sides of the first welding rib 41, there are provided first concave grooves 51, 52 for accommodating welding burrs generated at the time of vibration welding between the first welding rib 41 and the second welding rib 42.
On both sides of the second welding rib 42, second concave grooves 53 and 54 are provided for accommodating welding burrs generated during vibration welding between the first welding rib 41 and the second welding rib 42.

The first concave groove 51 communicates with the second concave groove 53 to form a rectangular annular inner space. This inner space is an inner burr pool for accumulating welding burrs generated at the time of vibration welding of the first and second welding ribs 41 and 42 without protruding inside, and one side of the first and second welding ribs 41 and 42. (Intake passage side, inside) The inner burr pool communicates with the intake passages 11 and 12 via the communication passage 56.
The first concave groove 52 communicates with the second concave groove 54 to form a rectangular annular outer space. This outer space is an outer burr pool for collecting the welding burrs generated at the time of vibration welding of the first and second welding ribs 41 and 42 without protruding to the outside, and one side of the first and second welding ribs 41 and 42. (On the opposite side to the intake passage side, outside). The outer burr pool communicates with the intake passages 11 and 12 through the communication passage 57.

Here, the protrusion-shaped first welding rib 41 provided on the flange 31 of the supporter 1 and the protrusion-shaped second welding rib 42 provided on the flange 32 of the casing 2 are joined by vibration welding.
Specifically, the outer peripheral surface of the flange 33 of the housing 3 is first brought into contact with the first locking portion of the flange 32 of the casing 2, and the end surface of the flange 33 of the housing 3 is first locked to the flange 32 of the casing 2. It abuts on the part.
Thereafter, the first welding rib 41 of the flange 31 of the supporter 1 and the second welding rib 42 of the flange 32 of the casing 2 are sandwiched by a pair of welding jigs, and the first welding rib 41 and the second welding rib 42 are butted together. The

Then, the first and second welding ribs 41 and 42 are relatively reciprocally slid on the joint surface between the first welding rib 41 and the second welding rib 42, thereby the first welding rib 41 and the second welding rib. The synthetic resin material in the vicinity of the joint surface with the rib 42 is partially melted by frictional heat.
Then, the first weld rib 41 and the second weld rib 42 are solidified (cured) again, so that the first and second weld ribs 41 and 42 are joined to each other by vibration welding. Integrated. During such vibration welding, a part of the melted synthetic resin material enters the inner burr pool and the outer burr pool. Thereby, it is possible to prevent welding burrs from protruding inside and outside the casing 2.

Therefore, the occurrence of problems such as deterioration of intake flow resistance (pressure loss), suction by the engine, and deterioration of the appearance (appearance, quality) of the casing 2 due to the protruding part of the welding burr is hindered. can do.
The weld burr 61 that has entered and hardened into the inner burr pool becomes an angular first locking portion that sandwiches the flange 33 of the housing 3 between the second locking portion of the flange 32 of the casing 2.

Each flange 32 of the casing 2 is provided with a second locking portion having an L-shaped cross section for locking in a state where the outer peripheral end of the flange 33 of the housing 3 is in contact.
The second locking portion of the flange 32 is formed integrally with the inner surface of the second welding rib 42. The second locking portion of the flange 32 has side walls (steps) 71 and 72 facing each other with a predetermined distance from the welding burr in the inner burr pool, and the periphery of the outer peripheral end of the flange 33 of the housing 3. Are provided with peripheral walls 73, 74, etc. surrounding the peripheral surface in the circumferential direction.
The steps 71 and 72 restrict the position of the flow direction (intake air flow direction) of intake air flowing through the inside of the housing 3 (intake air passage 12) when the flange 33 of the housing 3 is in direct contact.
The peripheral walls 73 and 74 restrict the position in the direction substantially orthogonal to the flow direction (intake air flow direction) of the intake air flowing through the inside of the housing 3 (intake air flow path 12) when the flange 33 of the housing 3 directly contacts.

On the flange 31 of the supporter 1, an angular ring-shaped rib 81 that protrudes toward the flange side of the casing 2 from an opposing surface located on the inner side (intake passage side) than the first and second welding ribs 41 and 42. Are provided.
The plurality of protruding ribs 81 are inner wall bodies provided on the inner side (inner side) than the first and second welding ribs 41 and 42. These protruding ribs 81 are provided so as to surround the intake passages 11 and 12. Note that tip surfaces (lower end surfaces shown in FIG. 4) of the plurality of protruding ribs 81 are opposed to the opposing surface of the flange 33 of the housing 3 with the communication passage 56 therebetween.

The flange 31 of the supporter 1 is a rectangular ring that protrudes toward the flange side of the casing 2 from a facing surface located on the outer side (opposite side to the intake passage side) of the first and second welding ribs 41 and 42. Each of the rib ribs 82 is provided.
The plurality of protruding ribs 82 are outer wall bodies provided on the outer side (outer side) than the first and second welding ribs 41 and 42. These projecting ribs 82 are provided so as to surround the outer burr pool. Note that the front end surfaces (lower end surfaces shown in FIG. 4) of the plurality of protruding ribs 82 are opposed to the opposing surfaces of the flange 32 of the casing 2 with the communication passage 57 interposed therebetween.

[Operation of Example 1]
Next, a method for controlling the valve opening of the tumble control valve (TCV) of this embodiment will be briefly described with reference to FIGS. 1 to 4A.

The ECU is a “tumble execution area” in which the tumble flow in the combustion chamber needs to be strengthened based on the engine operating status, for example, the engine speed (engine speed) and the engine load (accelerator opening or throttle opening). Or whether the tumble flow in the combustion chamber does not need to be strengthened.
The required tumble ratio is obtained based on the engine operating status, for example, the engine rotation speed and the engine load. When the required tumble ratio is equal to or greater than a predetermined value, the plurality of rotary valves are fully closed, and the required tumble ratio is less than the predetermined value. Sometimes a plurality of rotary valves may be fully opened.

When the ECU determines that it is the “tumble execution area”, it controls the power supplied to the motor (for example, energizes the motor). At this time, since the plurality of rotary valves are driven in the valve closing operation direction using the motor torque, the plurality of rotary valves are closed. That is, as shown in FIG. 2, the curved surface portions 15 of the valve plates 8 of the plurality of rotary valves are controlled to be opened and closed (fully closed) so as to be in the fully closed position (fully closed state). At this time, the flow path opening cross-sectional area of each intake passage 11-13 becomes the minimum. Further, when the plurality of rotary valves are fully closed, a slight gap (clearance) is formed between the curved surface portion 15 of the rotary valve and the end surface portion 24 of the housing 3 and the intake outlet portion of the intake passage 12.
In this case, the intake air flow that flows from the upstream end of the intake manifold to the downstream end (intake passages 11 and 12) flows along the concave curved surface of each curved surface portion 15 of the plurality of rotary valves, It flows into the opening 16 opened at the top of the valve plate 8.

Then, the intake air flow that flows into the opening 16 is blown into the intake passage 13 from the opening 16 and becomes a drift that flows along the flow path wall surface in the center in the width direction of the upper wall portion of the casing 2.
The drift flowing through the upper wall portion of the intake passage 13 is introduced into the upper layer portion of the intake port of the cylinder head from the upper wall portion side of the intake outlet portion of the intake passage 13, and flows into the channel wall surface of the upper layer portion of the intake port. It flows along.
And the intake flow which flows along the flow path wall surface of the upper part of the intake port is supplied into the combustion chamber from the intake port opening. At this time, since a tumble flow is generated in the combustion chamber for each cylinder of the engine, the combustion efficiency in the combustion chamber at the time of engine start or idling operation is improved, and fuel consumption and emission (for example, HC reduction effect) are improved. The

On the other hand, when the ECU determines that it is the “tumble non-execution region”, the power supplied to the motor is controlled (for example, the motor is energized). At this time, since the plurality of rotary valves are driven in the valve opening operation direction using the motor torque, the plurality of rotary valves are opened. That is, as shown in FIG. 3, the valve plates 8 of the plurality of rotary valves open the intake passages 11 to 13 and are formed between the lower wall portion of the casing 2 and the lower wall portion of the housing 3. Opening / closing control (full open control) is performed so that the storage posture (stored state, fully open state) stored in the recess 14 is obtained. At this time, the flow path opening cross-sectional area of each intake passage 11-13 becomes the maximum.
In this case, the intake air flow that flows from the upstream end of the intake manifold to the downstream end (intake passages 11 and 12) passes straight through the intake passage 13 and is taken from the intake outlet of the intake passage 13. Introduced in the port. The intake air flow that has passed through the intake port is supplied into the combustion chamber from the intake port opening. At this time, no tumble flow is generated in the combustion chamber.

[Effect of Example 1]
As described above, in the intake device (intake vortex generator) of the internal combustion engine of the present embodiment, the second locking portion (steps 71, 72, peripheral walls 73, 74) of the flange 32 of the casing 2 is connected to the housing 3. As shown in FIG. 4A, the flange 33 is fitted and fixed to the jig so that the flanges 32 and 33 are located on the top side (upper side in the drawing). The flange 31 of the supporter 1 is placed on the flanges 32 and 33, the first welding rib 41 of the supporter 1 and the second welding rib 42 of the casing 2 are butted, and the tips of the first and second welding ribs 41 and 42 are brought together. The parts are vibration welded.

At this time, a part of the melted synthetic resin material enters the inner burr pool and the outer burr pool. The first and second welding ribs 41 and 42 are joined by solidifying the melted portion again. In addition, the welding burr that flows out into the inner burr pool and fills in the inner burr pool is also cured to form a square annular welding burr (first locking portion) 61.
Then, the welding burr 61 that has entered and hardened into the inner burr pool formed between the first and second concave grooves 51 and 53 and the second locking portion (steps 71, 72, etc.) of the flange 32 of the casing 2 are formed. The flange 33 of the housing 3 is sandwiched and held therebetween. Thereby, the supporter 1, the casing 2, and the plurality of housings 3 are integrated to manufacture the downstream end portion (intake duct) of the intake manifold.

Thus, during the vibration welding process in which the first welding rib 41 of the supporter 1 and the second welding rib 42 of the casing 2 are vibration welded, the end face portion 24 of the housing 3 and the intake outlet portion of the intake passage 12 and the valve plate of the rotary valve. There is no need to provide an extra amplitude clearance between the eight curved surface portions 15. Thereby, since the physique of the whole intake eddy current generator can be reduced in size, the mountability of the intake eddy current generator on a vehicle such as an automobile can be improved.
Moreover, the supporter 1, the casing 2, and the housing 3 divided into at least three can be fixed at low cost.

Moreover, since the welding shift | offset | difference for every product between the 1st welding rib 41 of the supporter 1 and the 2nd welding rib 42 of the casing 2 can be prevented, the state which positioned the housing 3 with respect to the casing 2 which has the accommodation recessed part 23 It can be fixed with. Thus, the gap between the end surface portion 24 of the housing 3 and the intake outlet portion of the intake passage 12 and the curved surface portion 15 of the valve plate 8 of the rotary valve does not vary from product to product, and the end surface portion 24 of the housing 3 and the intake passage 12 are not varied. This makes it possible to make the gap between the intake outlet portion and the curved surface portion 15 of the valve plate 8 of the rotary valve uniform.
Therefore, in the intake vortex generator having the tumble control valve that adjusts the tumble flow generated in the combustion chamber for each cylinder of the engine by opening and closing operation, the tumble flow in the combustion chamber for each cylinder of the engine is further strengthened. Can be planned. As a result, it is possible to improve combustion efficiency and fuel consumption by stabilizing combustion.

  FIG. 4B shows a second embodiment of the present invention, and is a diagram showing a housing vibration welding and fixing structure for a casing.

As in the first embodiment, the intake duct of the present embodiment includes a supporter 1, a casing 2, and a housing 3 that are divided into at least three parts. The supporter 1, the casing 2, and the housing 3 are all integrally formed of a synthetic resin such as a thermoplastic resin (for example, polyamide resin: PA).
The supporter 1 and the casing 2 are respectively provided with flanges 31 and 32 that are arranged to face each other with a space such as an inner side or an outer side burr pool. The housing 3 is provided with a flange 33 that is disposed to face the flange 31 of the supporter 1 with a space such as an inner burr pool or the like interposed therebetween. The flange 32 is disposed so as to surround the flange 33 of the housing 3 in the circumferential direction.

The supporter 1 and the casing 2 are respectively provided with first and second welding ribs 41 and 42 which are brought into contact with each other and vibration welded.
The supporter 1 includes a ridge rib 83 that protrudes toward the flange side of the housing 3 from the flange 31 that is located closer to the intake passage side (inner side) than the first and second welding ribs 41 and 42. The front end surface of the protruding rib 83 is in direct contact (contact) with the opposing surface of the flange 33 of the housing 3.
As in the first embodiment, the outer peripheral end of the flange 33 of the housing 3 is interposed between the weld burr 61 that has entered and hardened into the inner burr pool and the second locking portion (step 72) of the flange 32 of the casing 2. It constitutes a fitting portion (locked portion) that is sandwiched and held.

As described above, in the intake vortex generator of this embodiment, the tip surface of the ridge rib 83 protruding from the flange 31 of the supporter 1 is in direct contact with the opposing surface of the flange 33 of the housing 3. The flange 33 of the housing 3 is sandwiched and held between the one protruding rib 83 and the second locking portion (step 72) of the flange 32 of the casing 2.
Thereby, the flange 33 of the housing 3 can be more reliably fixed to the flange 31 of the supporter 1 and the flange 32 of the casing 2.

  FIG. 5A shows a third embodiment of the present invention, and is a diagram showing a housing vibration welding and fixing structure for a casing.

Unlike the second embodiment, the housing 3 of the present embodiment protrudes from the flange 33 located on the intake passage side (inner side) of the first and second welding ribs 41 and 42 toward the flange side of the supporter 1. A ridge rib 84 is provided. The front end surface of the protruding rib 84 is in direct contact (contact) with the opposing surface of the flange 31 of the supporter 1.
As in the first embodiment, the outer peripheral end of the flange 33 of the housing 3 is interposed between the weld burr 61 that has entered and hardened into the inner burr pool and the second locking portion (step 72) of the flange 32 of the casing 2. It constitutes a fitting portion (locked portion) that is sandwiched and held.

As described above, in the intake vortex generator of the present embodiment, the tip surface of the rib rib 84 protruding from the flange 33 of the housing 3 is in direct contact with the opposing surface of the flange 31 of the supporter 1. The flange 33 and the projecting rib 84 of the housing 3 are sandwiched and held between the first flange 31 and the second locking portion (step 72) of the flange 32 of the casing 2.
Thereby, the flange 33 of the housing 3 can be more reliably fixed to the flange 31 of the supporter 1 and the flange 32 of the casing 2.

  FIG. 5B shows a fourth embodiment of the present invention, and is a diagram showing a housing vibration welding and fixing structure for a casing.

The supporter 1 and the casing 2 of the present embodiment include first and second welding ribs 41 and 42 that protrude from the flanges 31 and 32 so as to face each other and that are butted against each other and vibration welded.
In the same manner as in the second embodiment, the supporter 1 has a rib rib 83 that protrudes toward the flange side of the housing 3 from the flange 31 that is located closer to the intake passage side (inner side) than the first and second welding ribs 41 and 42. It has. The front end surface of the protruding rib 83 is in direct contact (contact) with the opposing surface of the flange 33 of the housing 3.

The housing 3 protrudes so as to face the first welding rib 41 from the flange 33 that is disposed to face the flange 31 of the supporter 1 with a space such as an inner burr pool, and the like, and the second welding rib 41. A third welding rib 43 is provided, which is brought into contact with the first welding rib 41 together with the welding rib 42 and vibration-welded.
The width of the welding surface of the first welding rib 41 is narrower than the width of the welding surface of the second and third welding ribs 42 and 43. That is, the width of the welding surface of the second and third welding ribs 42 and 43 is made wider than the width of the welding surface of the first welding rib 41.

On both sides of the first welding rib 41, there are provided first concave grooves 51 and 52 for accommodating welding burrs generated during vibration welding between the first welding rib 41 and the second and third welding ribs 42 and 43. It has been.
Next to the second and third welding ribs 42 and 43, there are second concave grooves for receiving welding burrs generated during vibration welding between the first welding rib 41 and the second and third welding ribs 42 and 43. 53 and 54 are provided.
The first concave groove 51 communicates with the second concave groove 53 to form a rectangular annular inner space. This inner space is an inner burr pool for accommodating the welding burrs generated at the time of vibration welding of the first to third welding ribs 41 to 43 without protruding inside, and the first to third welding ribs 41 to 43 Provided on one side (intake passage side, inside).

As in the first embodiment, the outer peripheral end of the flange 33 of the housing 3 is interposed between the weld burr 61 that has entered and hardened into the inner burr pool and the second locking portion (step 72) of the flange 32 of the casing 2. It constitutes a fitting portion (locked portion) that is sandwiched and held.
As described above, in the intake vortex generator of the present embodiment, the supporter 1, the casing 2 and the housing 3 divided into at least three can be welded and joined at the same time, so that the flange 31 of the supporter 1 and the flange 32 of the casing 2 are joined. The flange 33 of the housing 3 can be more reliably fixed.

  FIG. 6 shows a fifth embodiment of the present invention, and is a view showing the generation range of weld burrs that have entered the inner burr pool and hardened.

The intake duct of the present embodiment is composed of a supporter 1, a casing 2, and a housing 3 that are divided into at least three, as in the first to fourth embodiments. The supporter 1, the casing 2, and the housing 3 are all integrally formed of a synthetic resin such as a thermoplastic resin (for example, polyamide resin: PA).
The supporter 1 and the casing 2 are respectively provided with flanges 31 and 32 that are arranged to face each other with a space such as an inner side or an outer side burr pool. The housing 3 is provided with a flange 33 that is disposed to face the flange 31 of the supporter 1 with a space such as an inner burr pool or the like interposed therebetween. The flange 32 is disposed so as to surround the flange 33 of the housing 3 in the circumferential direction.

The supporter 1 and the casing 2 are provided with first and second welding ribs 41 and 42 which protrude from the flanges 31 and 32 so as to face each other and are brought into contact with each other and subjected to vibration welding. These first and second welding ribs 41 and 42 are provided so as to surround a periphery of an inner burr pool described later.
In the present embodiment, the weld burrs 61 to 64 that have entered and hardened into the inner burr pool are partially installed in the circumferential direction surrounding the intake passages 11 and 12.
As described above, the intake vortex generator of the present embodiment can achieve the same effects as those of the first to fourth embodiments.

[Modification]
In this embodiment, the present invention is applied to an intake vortex generator that generates a vertical swirling flow (tumble flow) in a combustion chamber of an internal combustion engine (engine). However, the present invention is applied to the internal combustion engine (engine). The present invention may be applied to an intake vortex generator that generates a lateral swirl flow (swirl flow) in the combustion chamber. Further, the present invention may be applied to an intake device capable of generating a squish vortex for promoting combustion of an internal combustion engine (engine).
In the present embodiment, the present invention is applied to an intake vortex generator, but the present invention is applied to an electronic throttle device for adjusting the flow rate of intake air sucked into an internal combustion engine (engine), and an intake passage of the internal combustion engine. The present invention may be applied to a variable intake device that changes the length or the sectional area of the intake passage.

In this embodiment, the actuator that drives the rotary valve that is the valve body of the intake control valve is configured by the electric actuator that includes the motor and the speed reduction mechanism. However, the actuator that drives the valve that is the valve body of the intake control valve Alternatively, it may be constituted only by a motor. Moreover, you may comprise by the negative-pressure actuated actuator provided with the electromagnetic or electric negative pressure control valve, or an electromagnetic actuator.
Note that valve urging means such as a spring for urging a plurality of valves in the valve opening operation direction or the valve closing operation direction may or may not be installed.

In this embodiment, the same synthetic resin material is used as the synthetic resin forming the supporter 1, the casing 2 and the housing 3 constituting the intake duct, but the synthesis forming the first to third divided bodies constituting the intake duct. Different synthetic resin materials may be used as the resin.
In this embodiment, the U-shaped rotary valve (or butterfly valve) is integrally formed of a metal material, but the U-shaped rotary valve (or butterfly valve) is integrally formed of a resin material. You may do it.

In addition, the present invention provides a valve unit (TCV) in which one valve is incorporated in one cartridge (housing) so as to be openable and closable. The present invention may be applied to a multiple integrated type valve opening / closing device (intake passage opening / closing device) arranged at a constant interval.
A diesel engine may be used as the internal combustion engine. Further, as the internal combustion engine, not only a multi-cylinder engine but also a single-cylinder engine may be used.

In the present embodiment, the present invention is applied to an intake vortex generator having an intake duct and a tumble control valve. However, the present invention is configured by an intake duct or an intake manifold that does not incorporate an intake control valve. The present invention may be applied to an intake device.
In the present embodiment, a structure is described in which at least three first to third divided bodies are assembled and fixed by abutting the tip of the first welding rib 41 and the tip of the second welding rib 42 and vibration welding. However, the tip of the first welding rib 41 and the tip of the second welding rib 42 are brought into contact with each other and welded using other welding methods such as heat welding, electric welding, ultrasonic welding, laser welding, etc., so that at least three The first to third divided bodies may be assembled and fixed.
Moreover, as a resin molding method of at least three first to third divided bodies, not only injection molding but also extrusion molding, blow molding, or the like may be used.

1 Supporter (first division)
2 Casing (second divided body)
3 Housing (third divided body, duct body)
4 Pin rod (shaft)
8 Valve plate (valve body)
31 Supporter flange (first counter part)
32 Flange of casing (second facing part)
33 Housing flange (third counter part)
41 First welding rib of supporter 42 Second welding rib of casing 43 Third welding rib of housing 51 First concave groove (inner burr pool)
52 1st groove (outside burr pool)
53 2nd groove (inner burr pool)
54 Second groove (outside burr pool)
61 Welding burr (first locking part)
62 Welding burr (first locking part)
63 Welding burr (first locking part)
64 Welding burr (first locking part)
71 Step (second locking part)
72 steps (second locking part)
73 Perimeter wall (second locking part)
74 Perimeter wall (second locking part)
81 Supporter ridge rib (inner wall)
82 Supporter ribs (outer wall)
83 Support rib rib 84 Housing rib rib

Claims (10)

Provided with an intake duct made of synthetic resin surrounding the intake passage through which intake air sucked into the internal combustion engine flows,
In the intake device for an internal combustion engine, wherein the intake duct is configured by first to third divided bodies divided into at least three parts,
The first and second divided bodies protrude from the first and second opposed portions so as to face each other, and face each other, and are arranged to face each other with a predetermined distance therebetween. Each having first and second welding ribs to be welded;
The first facing portion has a burr pool for accommodating a welding burr generated at the time of welding the first welding rib and the second welding rib, between the second facing portion and the second facing portion.
The intake device for an internal combustion engine, wherein the third divided body has a fitting portion that is sandwiched between the weld burr that has entered and hardened into the burr pool and the second facing portion. The intake device for an internal combustion engine according to claim 1,
The intake device for an internal combustion engine, wherein the second facing portion has a locking portion that locks the fitting portion. The intake device for an internal combustion engine according to claim 1 or 2,
The third divided body includes a third facing portion that is disposed to face the first facing portion with a predetermined distance therebetween.
The first divided body has a ridge rib that protrudes from the first facing portion toward the third facing portion side, located closer to the intake passage side than the first and second welding ribs,
An intake device for an internal combustion engine, wherein a tip of the protruding rib is in contact with the third facing portion. The intake device for an internal combustion engine according to claim 1 or 2,
The third divided body is positioned closer to the intake passage than a third facing portion and the first and second welding ribs disposed to face each other with a predetermined distance from the first facing portion. , Having a rib rib projecting from the third facing portion toward the first facing portion side,
An intake device for an internal combustion engine, wherein a tip of the protruding rib is in contact with the first facing portion.   The intake device for an internal combustion engine according to any one of claims 1 to 4, wherein the third divided body is disposed to face the first opposed portion with a predetermined distance therebetween. And a third welding rib protruding from the third facing portion so as to face the first welding rib and being abutted against the first welding rib together with the second welding rib. An intake device for an internal combustion engine, comprising:   6. The intake device for an internal combustion engine according to claim 1, further comprising an intake control valve that controls intake air flowing through the intake passage by an opening / closing operation. Intake device. The intake device for an internal combustion engine according to claim 6,
The intake control valve is a rotational operation that is a rotation axis that extends in a direction orthogonal to the direction of intake air flow in the intake duct and a curve of a radius of curvature centered on a central point located on the central axis of the rotation axis An intake device for an internal combustion engine, comprising a rotary valve that reciprocates on a line. The intake device for an internal combustion engine according to claim 7,
The intake system for an internal combustion engine, wherein the third divided body has a duct body in which the intake passage is formed. The intake device for an internal combustion engine according to claim 8,
The intake device for an internal combustion engine, wherein the second divided body has a bearing portion that supports the rotating shaft. The intake device for an internal combustion engine according to claim 9,
The intake passage has an outlet portion opened at a downstream end surface in the intake flow direction of the duct body,
An intake device for an internal combustion engine, wherein the rotary valve has a facing portion that is opposed to the outlet portion of the duct body with a gap when fully closed.

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