JP2008045430A - Multiple integral valve opening-closing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To absorb a variation in valve opening between cylinders of an engine, when fully closing a valve, without increasing rigidity of a pin rod itself. <P>SOLUTION: A valve installing angle θv with respective valve holding parts of respective intake flow control valves 1 corresponding to the respective valve holding parts of the pin rod, is set so as to become large stepwise in order near in a distance from a stopper lever. Actually, a set angle θv of respective square holes 45 formed in response to respective valve stems 46, is set so as to become large stepwise in order near in the distance from the stopper lever, to the respective valve stems 46 arranged for every one of a plurality of intake flow control valves 1. Thus, since strength of a main intake flow of passing through a main opening part of the respective intake flow control valves 1 can be restrained from becoming different between the cylinders of the engine, degradation of engine performance can be prevented. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a multiple integrated valve opening / closing device in which a plurality of air flow control valves are arranged in the direction of the rotation axis of a polygonal cross-section shaft inside an intake manifold of an internal combustion engine.

[Conventional technology]
2. Description of the Related Art Conventionally, an intake control device for an internal combustion engine in which a plurality of valves coupled by a single shaft are arranged inside an intake manifold of the internal combustion engine is known (for example, Patent Document 1). An intake control device for an internal combustion engine in which a plurality of valve units are arranged in parallel in the direction of the rotation axis of the shaft at regular intervals inside an intake manifold of the internal combustion engine is also known (for example, Patent Document 2). This valve unit includes one housing and one valve.
Here, each valve described in Patent Documents 1 and 2 is integrally formed of a resin material, and a cylindrical valve shaft that forms the center of rotation is provided with a through-hole penetrating in the rotation axis direction. Yes.

  Moreover, the shafts described in Patent Documents 1 and 2 are polygonal cross-section shafts, which are inserted into the through holes formed for each of the plurality of valves, so that the plurality of valves are coupled in a skewered state. . The cross section of the through hole is formed in the same shape as the cross section of the polygonal shaft. Thereby, when a shaft is inserted into the through hole of each valve, relative rotation between each valve and the shaft is limited. Each valve uses a type in which plate-like valve bodies are formed on both sides in the radial direction perpendicular to the rotation axis direction of the valve shaft, that is, a butterfly valve.

  Further, in the case of the intake control device for an internal combustion engine described in Patent Documents 1 and 2, since a plurality of valves are coupled so as to be skewered by a single shaft, the shafts are fitted to the respective valves. It is desirable to provide a stopper portion on one end side in the rotational axis direction than the portion. When the valve is fully closed, the stopper portion of the shaft is brought into contact with and locked to a fully closed stopper member provided on the intake manifold side, so that all valve openings are regulated to a predetermined fully closed opening. . The fully closed opening is a valve opening that provides a predetermined leakage air flow rate when the valve is fully closed.

  An intake manifold of the internal combustion engine is provided with one actuator that collectively changes all valve openings. When one end portion of the shaft in the rotation axis direction and the output shaft of the actuator are coupled via a coupling member, the power in the actuator is determined if there is no predetermined gap between the coupling member and the output shaft. The driving force of the source (for example, an electric motor) is not smoothly transmitted to the shaft. For this reason, there is a possibility that the shaft and the coupling member may become loose due to the gap between the coupling member and the output shaft.

In particular, when vehicle vibration, engine vibration, or intake pulsation vibration pressure in the intake pipe of the engine is transmitted to the intake manifold, the coupling member is severely rattled, and the output shaft repeatedly collides or frictions with the coupling surface of the coupling member. The fitting surface of the coupling member may be abnormally worn.
Therefore, for the purpose of suppressing backlash of the coupling member, a spring load is applied to the side opposite to the actuator side in the direction of the rotation axis of the shaft, and to the side that reduces the gap between the coupling member and the output shaft. It is desirable to install a backlash spring that provides

[Conventional technical problems]
However, in the intake control device for an internal combustion engine described in Patent Documents 1 and 2, during the operation of the engine, when all the valves are fully closed (when the valves are fully closed), When intake negative pressure acts on the surface of the plate-like valve body, load torque (bending moment) is applied in the valve opening operation direction around the valve shaft of each valve. As a result, a twist corresponding to the magnitude of the load torque is generated in each fitting portion that holds and fixes the valve shaft of each valve in the shaft. The twist of each fitting portion of the shaft is different from the valves described in Patent Documents 1 and 2, and the valve shaft forming the rotation center of each valve is deviated to one side in the valve surface direction of each plate-like valve body. This is more noticeable in the case of a portable valve.

  In addition, in the case of an intake control device for an internal combustion engine equipped with a backlash spring, if the spring load of the backlash spring is applied to the shaft, the load in the valve opening operation direction around the valve shaft of each valve is also the same. Torque (bending moment) is applied. Thereby, the twist corresponding to the magnitude | size of load torque generate | occur | produces in a shaft.

  Here, when the valve is fully closed, if the shaft fitting parts are twisted at different twist angles by the load torque acting in the valve opening operation direction for each valve, the intake port for each cylinder of the engine Deviation occurs in the fully closed opening degree of each valve arranged corresponding to each of a plurality of intake passages connected independently. That is, since the fully closed opening of the valve varies among engine cylinders, the strength of the intake air flow differs between engine cylinders, and the leakage air flow rate when the valve is fully closed varies among engine cylinders. .

  Here, the torsion angle of each fitting portion that holds and fixes the valve shaft of each valve on the shaft increases stepwise in order of increasing distance from the stopper portion that regulates the fully closed opening degree when the valve is fully closed. That is, when the fully closed opening of the valve closest to the stopper is the reference opening, the fully closed opening of the valve is larger than the reference opening as the distance from the stopper increases. As the distance from the stopper portion increases, the strength of the intake air flow decreases, and as the distance from the stopper portion increases, the leakage air flow rate when the valve is fully closed increases. For this reason, the problem of deteriorating engine performance arises.

  In order to eliminate the variation (deviation) of the valve opening between the cylinders of the engine, it is necessary to suppress the deviation of the twist angle of each fitting portion of the shaft. For this reason, it is necessary to increase the rigidity of the shaft itself. However, if the outer diameter of the shaft is increased in order to increase the rigidity of the shaft itself, each through hole is increased as the diameter of each through hole provided for each of the plurality of valves is increased. The size of each valve shaft arranged so as to surround the hole increases. If the outer diameter of the shaft is increased and each valve shaft is further increased in size, the material cost increases correspondingly and the cost increases.

Further, since the weight of the valve and the shaft increases, the vibration resistance of the valve (or valve unit) is lowered. For this reason, when vehicle vibration, engine vibration, or intake pulsation vibration pressure in the intake pipe of the engine is transmitted to the intake manifold (or housing), the valve is severely rattled, causing collision or friction between the valve and the intake manifold (or housing). Repeatedly, the valve and intake manifold (or housing) may be abnormally worn.
JP-A-2004-060525 (page 1-7, FIG. 1 to FIG. 3) Japanese translation of PCT publication No. 2003-509634 (page 1-9, FIG. 1 to FIG. 6)

  An object of the present invention is to prevent the deterioration of the performance of the internal combustion engine by absorbing the variation in the valve opening between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft itself. An object of the present invention is to provide a continuous integral type valve opening / closing device.

  According to the first aspect of the present invention, a plurality of air flow paths that are independently connected to each cylinder of the internal combustion engine are formed inside the casing, and a plurality of air flow paths corresponding to each of these air flow paths are formed. The valve is housed in an openable and closable manner. Then, by inserting one shaft into each through hole formed for each of the plurality of valves, the plurality of valves are coupled by a single shaft so as to be skewered. Thereby, the opening degree of a some valve | bulb (all valves) can be collectively changed with one actuator. A plurality of fitting portions for holding a plurality of valves at a predetermined mounting angle are provided on one shaft.

The mounting angle of each valve corresponding to each of the plurality of fitting portions with respect to each of the plurality of fitting portions is an angle corresponding to the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. By setting so that the load torque in the different valve opening operating directions is applied to each valve arranged corresponding to each cylinder (each air flow path) of the internal combustion engine. Even when the valve is fully closed, the opening degree of each valve (all the valves connected to one shaft so as to be skewered) becomes substantially the same valve opening degree.
Thereby, it is possible to absorb the variation in the valve opening between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft itself. Therefore, it can suppress that the strength of an airflow differs between the cylinders of an internal combustion engine. In addition, since it is possible to suppress a difference in the leakage air flow rate between the cylinders of the internal combustion engine when the valve is fully closed, it is possible to prevent a decrease in the performance of the internal combustion engine without increasing the size of the shaft and increasing the cost. .

According to the invention of claim 2, claim 11, claim 16, claim 20, claim 25, and claim 28, each valve corresponding to each of the plurality of fitting portions surrounds the periphery of the through hole. A cylindrical valve shaft disposed in this manner and a plate-shaped valve body extending from the valve shaft in a radial direction perpendicular to the rotation axis direction are provided.
According to invention of Claim 3, Claim 12, Claim 17, Claim 21, Claim 26, Claim 29, as each valve corresponding to every some fitting part, a valve shaft is a plate-shaped valve. A cantilever valve that is biased to one side of the valve surface direction perpendicular to the body thickness direction is used.

According to the invention of claim 4, claim 13, claim 16, claim 22, claim 27, and claim 30, a part of each plate-like valve body provided for each of a plurality of valves, particularly a plurality of An opening for generating a vortex in the intake air supplied to the cylinder of the internal combustion engine by notching an end face (end face of each plate-like valve body) opposite to each valve shaft provided for each valve. Provided.
According to the fifth aspect of the present invention, the mounting angle of each valve corresponding to each of the plurality of fitting portions with respect to each of the plurality of fitting portions is set so that the opening degrees of all the valves when the valves are fully closed are substantially the same. The effect similar to that of the first aspect of the invention can be achieved by setting the valve opening.

According to the invention described in claims 6, 14, 18, and 23, one side of the shaft in the direction of the rotation axis (for example, an actuator) from the range of the shaft inserted into each through hole of each of the plurality of valves. On the side opposite to the actuator side or the actuator side), there is a stopper part that regulates the valve opening when the valve is fully closed.
According to the seventh aspect of the present invention, the mounting angle of each valve corresponding to each of the plurality of fitting portions with respect to each of the plurality of fitting portions is increased stepwise in order of increasing distance from the stopper portion. By setting, the opening degree of all the valves when the valve is fully closed becomes substantially the same valve opening degree. Thus, the same effect as that attained by the 1st aspect can be attained.
According to invention of Claim 8 and Claim 31, the cross-sectional shape of each fitting part provided in a shaft is formed in polygonal cross-sectional shape. Moreover, the hole shape of each through-hole formed for every some valve | bulb is formed in the polygonal hole shape.

  According to the ninth aspect of the present invention, a cylindrical valve is provided so as to surround each of the through holes formed for each of the plurality of valves in each of the valves attached corresponding to the plurality of fitting portions of the shaft. A shaft is provided. Then, for each valve shaft provided for each of the plurality of valves, the set angle of each through hole formed corresponding to each valve shaft is increased stepwise in order of increasing distance from the stopper portion. By setting, the opening degree of all the valves when the valve is fully closed becomes substantially the same valve opening degree. Thus, the same effect as that attained by the 1st aspect can be attained.

According to the tenth and thirty-sixth aspects of the present invention, the plurality of fitting portions provided corresponding to the plurality of valves at a constant interval in the rotation axis direction of the shaft are formed for the plurality of valves. It is inserted inside each through hole. That is, the plurality of valves are attached at a predetermined attachment angle corresponding to each of the plurality of fitting portions at a constant interval in the rotation axis direction of the shaft.
According to invention of Claim 10, the angle of the insertion surface of each fitting part inserted in each through-hole formed for every some valve | bulb becomes large in steps in order with the near distance from a stopper part. By setting in this way, the opening degrees of all the valves when the valves are fully closed become substantially the same valve opening degree. Thus, the same effect as that attained by the 1st aspect can be attained.

According to the eleventh aspect of the present invention, the rigidity of each plate-like valve body provided for each of the plurality of valves is set to a rigidity corresponding to the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. When a load torque in a different valve opening operation direction is applied to each valve disposed corresponding to each cylinder (for each of a plurality of air flow paths) of the internal combustion engine. Even so, the rigidity of each plate-like valve body becomes higher corresponding to the magnitude of the load torque acting on each plate-like valve body, and the torsion angle for each fitting portion of the shaft is set to all fitting portions. Therefore, the opening degree of each valve (all the valves coupled so as to be skewered on one shaft) when the valve is fully closed becomes substantially the same valve opening degree.
Thereby, it is possible to absorb the variation in the valve opening between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft itself. Therefore, it can suppress that the strength of an airflow differs between the cylinders of an internal combustion engine. In addition, since it is possible to suppress a difference in the leakage air flow rate between the cylinders of the internal combustion engine when the valve is fully closed, it is possible to prevent a decrease in the performance of the internal combustion engine without increasing the size of the shaft and increasing the cost. .

According to the fifteenth aspect of the present invention, each plate-like valve body provided for each of the plurality of valves has a predetermined thickness on each valve shaft side (the shaft peripheral portion) provided for each of the plurality of valves. Thick part is provided. Here, each thick part provided for each plate-shaped valve body may be a portion where the plate thickness is the largest among the respective plate-shaped valve bodies, and each valve in each plate-shaped valve body. It may be a location where the plate thickness is larger than the end edge (valve end edge) opposite to the shaft side.
And by setting the plate thickness of each thick part provided for each plate-like valve body so as to decrease stepwise in order from the shortest distance from the stopper part, each plate-like provided for each of a plurality of valves The rigidity of the valve body increases stepwise in order of increasing distance from the stopper portion. Thus, the same effect as that attained by the 11th aspect can be attained.

According to the invention described in claim 16, the opening area of each opening formed for each plate-like valve body corresponds to the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. By setting so that the opening area becomes the same, a load torque in a different valve opening operation direction is generated for each valve arranged corresponding to each cylinder (for each of the plurality of air flow paths) of the internal combustion engine. Opening of each opening formed for each plate-like valve body of each valve (all valves coupled so as to be skewered to one shaft) even when the valve is fully closed The opening areas are substantially the same.
Thereby, it is possible to absorb the variation in the opening area of each opening between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft itself. Therefore, it can suppress that the strength of an airflow differs between the cylinders of an internal combustion engine. In addition, since it is possible to suppress a difference in the leakage air flow rate between the cylinders of the internal combustion engine when the valve is fully closed, it is possible to prevent a decrease in the performance of the internal combustion engine without increasing the size of the shaft and increasing the cost. .

  According to the invention described in claim 19, by setting the opening area of each opening formed for each plate-shaped valve body so as to increase stepwise in order of increasing distance from the stopper portion, The opening areas of the openings of all the valves when fully closed are substantially the same opening area. Thus, the same effect as that attained by the 16th aspect can be attained.

According to the twentieth aspect of the present invention, the flow path cross-sectional area of each air flow path is reduced on the flow path wall surface in the vicinity of the fully closed position of each valve for each of the plurality of cylindrical portions provided in the casing ( Protrusions projecting to the rotation center position side of each valve and the valve shaft side of each valve are provided.
And the top face of each convex part provided for every plurality of cylinder parts is used as an opposing face which counters the end face of each plate-like valve element provided for every plurality of valves when the valve is fully closed.
In other words, the opposing surface of each convex portion has a direction in which the cross-sectional area of each air channel is reduced with respect to the upstream or downstream channel wall surface in the air flow direction relative to this opposing surface (each valve It is provided at a high position protruding to the rotation center position side and the valve shaft side of each valve.
Then, the distance between the rotational center position of each valve and the position of the opposing surface of each convex portion (height of each convex portion for each of the plurality of cylindrical portions) is the valve opening operation direction for each valve when the valve is fully closed. By setting the distance (height) corresponding to the load torque acting on the engine, for each valve arranged corresponding to each cylinder (each air flow path) of the internal combustion engine, Each plate-like valve body of each valve (all valves coupled so as to be skewered to one shaft) when the valve is fully closed even when load torque is applied in different valve opening operation directions The opening area of each gap formed between the end face of each of the plurality of air flow paths and the opposing surfaces provided for each of the plurality of air flow paths is substantially the same opening area.
Thereby, it is possible to absorb the variation in the opening area of each gap between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft itself. Therefore, it can suppress that the strength of an airflow differs between the cylinders of an internal combustion engine. In addition, since it is possible to suppress a difference in the leakage air flow rate between the cylinders of the internal combustion engine when the valve is fully closed, it is possible to prevent a decrease in the performance of the internal combustion engine without increasing the size of the shaft or increasing the cost. .

  According to the invention described in claim 24, by setting the distance between the rotation center position of each valve and the position of the opposing surface of each convex part so as to increase stepwise in order of increasing distance from the stopper part. When the valves are fully closed, the opening areas of the gaps formed between the end surfaces of the plate-like valve bodies of the valves and the opposing surfaces are substantially the same. Thus, the same effect as that attained by the 20th aspect can be attained.

According to the twenty-fifth aspect of the present invention, each plate-like valve body provided for each of the plurality of valves has an end surface vicinity (valve edge portion) opposite to each valve shaft side provided for each of the plurality of valves. In addition, a protruding portion curved in an arc shape is provided so as to follow the rotation trajectory of each plate-like valve body. And each projection part provided for every plate-shaped valve body of all the valves protrudes in the valve closing operation direction of each valve with respect to the valve surface on the valve shaft side from this projection part.
And the amount of protrusion in the valve closing direction of each projection provided for each plate-like valve element of all valves is generated by the load torque that acts in the valve opening direction for each valve when the valve is fully closed. By setting the projecting amount corresponding to the maximum value of the shaft twisting angle, the valve opening operation is different for each valve arranged corresponding to each cylinder (each air flow path) of the internal combustion engine. Even when a load torque is applied in the direction, it is provided for each plate-like valve body of each valve (all valves coupled so as to be skewered on one shaft) when the valve is fully closed. The opening area of each gap formed between each protrusion and each channel wall surface provided for each of the plurality of air channels is substantially the same opening area.
Thereby, it is possible to absorb the variation in the opening area of each gap between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft itself. Therefore, it can suppress that the strength of an airflow differs between the cylinders of an internal combustion engine. In addition, since it is possible to suppress a difference in the leakage air flow rate between the cylinders of the internal combustion engine when the valve is fully closed, it is possible to prevent a decrease in the performance of the internal combustion engine without increasing the size of the shaft and increasing the cost. .

According to the twenty-eighth aspect of the present invention, the flow path wall surface in the vicinity of the fully closed position of each valve for each of the plurality of cylindrical portions provided in the casing is each plate-like valve provided for each of the plurality of valves when the valve is fully closed. It is used as a facing surface that faces the end surface of the body.
And each opposing surface provided for every some cylinder part is extended in the valve opening operation direction of each valve with respect to the flow-path wall surface of the upstream of an air flow direction rather than this opposing surface. Moreover, each opposing surface provided for every some cylindrical part is curving in circular arc shape so that the rotation locus | trajectory of each plate-like valve body provided for every some valve | bulb may be followed.
Then, the curved surface length in the valve opening operation direction of each facing surface is curved corresponding to the maximum value of the shaft twist angle generated by the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. When the load torque in different valve opening operation directions is applied to each valve arranged corresponding to each cylinder (each plurality of air flow paths) of the internal combustion engine by setting the surface length Even so, it is provided for each of the plurality of air flow paths and the end face of each plate-like valve body of each valve (all valves coupled so as to be skewered on one shaft) when the valve is fully closed. The opening area of each gap formed between the opposing surfaces is substantially the same opening area.
Thereby, it is possible to absorb the variation in the opening area of each gap between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft itself. Therefore, it can suppress that the strength of an airflow differs between the cylinders of an internal combustion engine. In addition, since it is possible to suppress a difference in the leakage air flow rate between the cylinders of the internal combustion engine when the valve is fully closed, it is possible to prevent a decrease in the performance of the internal combustion engine without increasing the size of the shaft and increasing the cost. .

According to a thirty-second aspect of the present invention, the actuator includes an output shaft coupled to one end portion of the shaft in the rotation axis direction. Here, a gap is formed in a coupling portion (coupling) between the output shaft of the actuator and one end portion of the shaft in the rotation axis direction.
According to the thirty-third aspect of the present invention, the spring disposed on the opposite side to the actuator side in the rotation axis direction of the shaft has the output shaft of the actuator and one end portion of the shaft in the rotation axis direction relative to the shaft. The load which urges | biass to the side which makes the clearance gap formed in the connection part small is provided. As a result, the gap between the coupling portion between the output shaft of the actuator and the one end portion of the shaft in the rotation axis direction is minimized, and shakiness of the shaft can be suppressed.
According to the invention of claim 34, as the casing, the valve units in which the valves are incorporated so as to be openable and closable inside the housing in which the air flow path is formed are arranged in a group at regular intervals in the rotation axis direction of the shaft. The intake manifold may be used.
According to a thirty-fifth aspect of the present invention, the shaft constitutes a rotation shaft that forms the rotation center of the plurality of valves.

The best mode for carrying out the present invention is to absorb the variation of the valve opening between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft. This is achieved by setting the mounting angle of each corresponding valve for each of multiple fitting parts so that it corresponds to the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. In addition, by setting the rigidity of each plate-like valve body provided for each of the plurality of valves so as to correspond to the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. It was realized.
Further, the purpose of absorbing the variation in the opening area of the opening between the cylinders of the internal combustion engine when the valve is fully closed without increasing the rigidity of the shaft is to open the opening of each opening formed for each plate-like valve body. This was realized by setting the area to be the opening area corresponding to the load torque acting in the valve opening operation direction for each valve when the valve was fully closed.
Also, the variation in the opening area of the gap formed between the flow path wall surface of the casing (or housing) between the cylinders of the internal combustion engine and each valve when the valve is fully closed is absorbed without increasing the rigidity of the shaft. The purpose is to determine the amount of protrusion in the valve closing direction of each projection provided for each plate-like valve element of all valves by the load torque that acts in the valve opening direction for each valve when the valve is fully closed. This is realized by setting the amount of protrusion corresponding to the maximum value of the generated shaft twist angle, and the curved surface length in the valve opening operation direction of each facing surface provided for each of the plurality of air flow paths This was realized by setting the length of the curved surface corresponding to the maximum value of the shaft twist angle generated by the load torque acting in the valve opening operation direction for each valve when closed.

[Configuration of Example 1]
1 to 6 show a first embodiment of the present invention. FIG. 1 is a view showing a set angle of a square hole with respect to a valve shaft, and FIG. 2 is a view showing an intake flow control device for an internal combustion engine. 3 and 4 are views showing an intake vortex generator (multiple integrated valve opening / closing device).

  The intake flow control device for an internal combustion engine according to the present embodiment promotes combustion of an air-fuel mixture in each cylinder of a multi-cylinder internal combustion engine (for example, a 4-cylinder gasoline engine: hereinafter referred to as an engine) mounted on a vehicle such as an automobile. It is provided with an intake vortex generator capable of generating a vertical intake vortex (tumble flow). In this intake vortex generator, a plurality of resin valves (hereinafter referred to as intake flow control valves) 1 to 4 are arranged in the direction of the rotation axis (rotation center axis) of a pin rod (shaft) 9 inside an intake manifold 5 constituting a common casing. (Multiple integrated type valve opening and closing device) arranged in parallel at regular intervals in the direction).

  An engine generates an output by heat energy obtained by burning a mixture of intake air and fuel in a combustion chamber, and an intake for supplying intake air (intake) into the combustion chamber of each cylinder of the engine. A duct (engine intake pipe) and an exhaust duct (engine exhaust pipe) for exhausting exhaust gas flowing out from the combustion chamber of each cylinder of the engine to the outside through an exhaust purification device are provided.

  Here, the intake duct is an air cleaner case that houses and holds an air cleaner (filtering element) that filters the intake air, a throttle body that is coupled downstream of the air cleaner case in the flow direction of the intake air, and an intake that is more than the throttle body A surge tank coupled to the downstream side in the air flow direction, and an intake manifold 5 having a double-pipe structure coupled to the downstream side in the intake air flow direction from the surge tank.

  The intake manifold 5 has a plurality of polygonal cylinder parts (first cylindrical part, first polygonal cylinder part) 6 having a plurality of fitting holes (first to fourth fitting holes) formed therein, and a plurality of insides. And a plurality of housings (second cylindrical portion of the casing, second polygonal cylindrical portion) 7 in which the intake passages (first to fourth intake passages) are formed. The intake manifold 5 distributes intake air that has flowed into the interiors (intake passages 11 and 12) of the plurality of polygonal cylinder portions 6 to intake ports 13 corresponding to the number of cylinders provided in the cylinder head 8 of the engine. However, it is made of resin for the purpose of weight reduction and cost reduction, and is integrally formed of a resin material (for example, a glass fiber reinforced thermoplastic resin).

  A plurality of fitting holes (valve unit accommodating portions, first to fourth fitting holes) 14 for accommodating and holding a plurality of valve units (cartridges) are respectively provided in the polygonal cylinder portion 6 of the intake manifold 5 of this embodiment. Is formed. Further, the polygonal tube portion 6 has two adjacent fitting holes 14 (for example, between the first and second fitting holes, between the second and third fitting holes, and between the third and fourth fitting holes). ) Are hermetically partitioned.

  Also, the intake manifold 5 has an intake flow of intake air flowing through the plurality of intake passages 12 from the left side wall portion of the polygonal cylinder portion 6 on the left end side in the drawing toward the right wall portion of the polygonal cylinder portion 6 on the right end side in the drawing. A plurality of shaft through holes 15 extending straight in a direction orthogonal to the direction (rotational axis direction, horizontal direction) are provided so as to penetrate all the fitting holes 14 and all the polygonal cylinder portions 6.

  Further, the inside of the plurality of polygonal cylinder portions 6, that is, the upstream side in the intake flow direction (intake air flow direction) with respect to each fitting hole 14 of the intake manifold 5, is connected independently for each cylinder of the engine. A plurality of intake passages (air passages) 11 are formed. A plurality of intake passages (air passages) 12 that are independently connected to each cylinder of the engine are formed inside the plurality of housings 7. Here, the plurality of intake passages 11 and 12 are independently connected to an intake port 13 for each cylinder of the engine.

  The engine forms a combustion chamber into which an air-fuel mixture is sucked from a cylinder head 8 that is airtightly coupled to the downstream end of the intake duct and an intake port 13 having a three-dimensional intake passage shape provided in the cylinder head 8. And a cylinder block (not shown). A spark plug (not shown) is attached to the cylinder head 8 so that the tip end portion is exposed in the combustion chamber of each cylinder. The cylinder head 8 is attached with an injector (internal combustion engine fuel injection valve, electromagnetic fuel injection valve: not shown) that injects fuel into the intake port 13 of each cylinder of the engine at an optimal timing. Yes.

  A plurality of intake ports 13 formed on one side of the cylinder head 8 are opened and closed by poppet-type intake valves (intake valves), and a plurality of exhaust ports (see FIG. (Not shown) is opened and closed by a poppet type exhaust valve (exhaust valve). Further, on the upstream side (intake manifold side) of the cylinder head 8 in the intake flow direction, a recess 16 is formed so as to protrude downward in the figure by the thickness of each intake flow control valve 1 to 4 for each of the plurality of valve units. Are integrally formed. Further, the cylinder head 8 has an angular annular coupling end surface facing the coupling end surface of the intake manifold 5.

  Between the cylinder head 8 and the intake manifold 5, a gasket 17 for sealing (sealing) an annular gap formed between the coupling end surface of the intake manifold 5 and the coupling end surface of the cylinder head 8 of the engine is mounted. ing. This gasket 17 is a rectangular annular (or rectangular annular) rubber-based elastic body (oil resistant rubber such as chloropyrene rubber: CR, nitrile rubber: NBR) surrounded by four sides of two sets of opposite sides.

Here, the intake passages (first intake passages) 11 and 12 and the intake port (first intake port) 13 that are opened and closed by the intake flow control valve 1 are independently connected to the engine cylinder (first cylinder) # 1. Has been. The intake passages (second intake passages) 11 and 12 and the intake port (second intake port) 13 that are opened and closed by the intake flow control valve 2 are independently connected to the engine cylinder (second cylinder) # 2. ing. The intake passages (third intake passages) 11 and 12 and the intake port (third intake port) 13 that are opened and closed by the intake flow control valve 3 are independently connected to the engine cylinder (third cylinder) # 3. ing. The intake passages (fourth intake passage) 11 and 12 and the intake port (fourth intake port) 13 opened and closed by the intake flow control valve 4 are independently connected to the engine cylinder (fourth cylinder) # 4. ing.
The first to fourth cylinders # 1 to # 4 may be the same as or different from the injection order of the fuel injected from the injectors installed corresponding to each cylinder of the engine.

  The intake vortex generator of this embodiment includes a valve unit in which one resin valve is opened and closed in one resin housing, and a rotating shaft of the pin rod 9 in each fitting hole 14 of the intake manifold 5. A plurality of intake flow control valve modules are arranged at regular intervals in the direction. These valve units are provided as many as the number of cylinders of the engine, are arranged corresponding to each cylinder of the engine, and are independently installed in the intake port 13 for each cylinder of the engine. In this embodiment, for example, a plurality of valve units are arranged in order from the front end to the rear end in the insertion direction of the pin rod 9.

  The plurality of valve units are all connected via a plurality of intake flow control valves 1 to 4 housed in the respective fitting holes 14 of the intake manifold 5 so as to be freely opened and closed (rotatable) and one pin rod 9. One valve drive device (actuator) 10 capable of collectively changing the valve opening (rotation angle) of the intake flow control valves 1 to 4 and intake air that is opened and closed by the intake flow control valves 1 to 4 inside. And a plurality of housings 7 in which passages 12 are formed.

  The plurality of housings 7 are all made of resin, and are integrally formed (resin integrated molding) into a rectangular shape (or rectangular shape) by a resin material (for example, a glass fiber reinforced thermoplastic resin). These housings 7 are elastically supported in the fitting holes 14 of the intake manifold 5 through two gaskets 18 and 19. Here, the two gaskets 18 and 19 have a function of sealing (sealing) an annular gap formed between the hole wall surface of each fitting hole 14 of the intake manifold 5 and the outer peripheral surfaces of the plurality of housings 7. It also has a function of attenuating engine vibration transmitted from the manifold 5 to each housing 7. The two gaskets 18 and 19 are rectangular ring-shaped (or rectangular ring-shaped) rubber-based elastic bodies (oil resistant rubber such as chloropyrene rubber: CR, nitrile rubber: surrounded by four sides of two sets of opposite sides. NBR).

The plurality of valve units are connected to the plurality of housings 7 corresponding to the intake passages 11 of the intake manifold 5 and connected to the intake ports 13 of the cylinder head 8. (First to fourth intake passages) 12 is provided. That is, a substantially rectangular intake passage 12 surrounded by four sides composed of two sets of opposite sides is formed inside each housing 7. These intake passages 12 are disposed downstream of the intake passage 5 in the intake manifold 5 in the intake flow direction, and communicate with combustion chambers for each cylinder of the engine via a plurality of intake ports 13.
A plurality of reinforcing ribs 20 extending in the direction parallel to the circumferential direction and the intake air flow direction are formed on the outer peripheral surface of each housing 7. These reinforcing ribs 20 may be omitted.

Here, the plurality of housings 7 are polygonal cylindrical bodies that accommodate the intake flow control valves 1 to 4 so as to be openable and closable, and constitute a polygonal cylindrical portion inside the intake manifold 5 having a double-pipe structure. Yes.
These housings 7 have a pair of upper and lower wall portions (top wall portion, bottom wall) on both sides (top and bottom sides) in a direction (top and bottom direction) orthogonal to the axial direction (intake flow direction) of each intake passage 12. Part: hereinafter referred to as housing upper and lower wall parts) 21 and 22 respectively. The plurality of housings 7 include a pair of left and right wall portions (both side wall portions, left and right side wall portions: hereinafter referred to as housings) on both sides in a direction (horizontal direction) substantially orthogonal to the axial direction (intake flow direction) of each intake passage 12. 23 and 24).

  In the plurality of housings 7, the passage wall surface (top wall surface) of each housing upper wall portion 21 and the passage wall surface (bottom wall surface) of each housing lower wall portion 22 are arranged to face each other with each intake passage 12 therebetween. Further, in the plurality of housings 7, the passage wall surface (side wall surface) of each housing left wall portion 23 and the passage wall surface (side wall surface) of each housing right wall portion 24 are opposed to each other with the intake passages 12 therebetween. . In the plurality of housings 7, the housing upper and lower wall portions 21 and 22 are longer (or shorter) than the housing left and right wall portions 23 and 24. Note that the four corners (corner portions) of each housing 7 are chamfered in an arc shape or an R shape, but the four corners (corner portions) of each housing 7 are formed in a right angle. May be.

  In addition, two valve bearing portions (cylindrical portions) are provided on the left and right wall portions 23 and 24 of the plurality of housings 7 so as to face each other with the intake passages 12 therebetween. Inside these valve bearing portions, there are formed two bearing receiving holes 25 that can rotatably accommodate each valve shaft (described later) formed for each of the plurality of intake flow control valves 1 to 4. .

  Here, the two valve bearing portions and the two bearing receiving holes 25 are provided on one side (the lower side in the drawing) of each housing 7 with respect to the central axis (the central axis of the intake passage 12) passing through the center of each intake passage 12 in the vertical direction in the drawing. , And offset on the bottom wall surface side, and offset on the upstream side of each intake passage 12 in the intake flow direction from the center of each intake passage 12 in the intake flow direction. That is, the two valve bearing portions and the two bearing receiving holes 25 are close to the upstream end of each housing 7 and close to the bottom wall surface (passage wall surface) of the housing lower wall portion 22 of each housing 7. It is arranged.

  Two bearings 26 and 27 are fitted and held by press-fitting or the like on the inner periphery of each bearing receiving hole 25 formed for each of the two valve bearing portions. The two bearings 26 and 27 are integrally formed in a cylindrical shape by a resin material or a metal material. Inside these bearings 26 and 27, both end portions (two valve sliding portions) in the rotational axis direction of each valve shaft formed for each of the plurality of intake flow control valves 1 to 4 are slidable in the rotational direction. Sliding holes for supporting each are formed.

  Here, the actuator 10 that drives the plurality of intake flow control valves 1 to 4 to close or open, as shown in FIGS. 3 to 6, is supplied with electric power to drive power (motor output shaft torque). An electric motor (not shown) that generates the power, and a power transmission mechanism (in this embodiment, a gear reduction mechanism: not shown) for transmitting the rotational motion of the motor shaft (output shaft) of this electric motor to the pin rod 9; It is an electric motor actuator provided with the power unit comprised including.

  As the electric motor, a direct current (DC) motor such as a brushless DC motor or a brushed DC motor is employed. An alternating current (AC) motor such as a three-phase induction motor may be used. The gear reduction mechanism reduces the rotational speed of the motor shaft of the electric motor so as to have a predetermined reduction ratio, and constitutes a power transmission mechanism that transmits the motor output shaft torque of the electric motor to the pin rod 9. The gear reduction mechanism includes a motor gear fixed to the motor shaft of the electric motor, an intermediate reduction gear that meshes with the motor gear, and a final reduction gear that meshes with the intermediate reduction gear. It is housed in the interior so that it can rotate freely.

  The actuator case 29 has a cylindrical fitting portion 31 that is fitted into the inner periphery of a sleeve-like cylindrical portion 30 that is integrally provided on the right side wall portion of the polygonal cylindrical portion 6 of the intake manifold 5. . A sealing material 32 such as an O-ring is attached between the cylindrical portion 30 and the fitting portion 31. The actuator case 29 rotatably supports an output shaft (shaft, gear shaft of the final reduction gear) 34 of the actuator 10 via a bearing part 33. The shaft 34 of the actuator 10 is connected to an end portion (one end portion) on one end side (actuator side) of the pin rod 9 in the rotation axis direction via a coupling member 35. The coupling member 35 has a fork portion coupled to one end portion of the pin rod 9 on the left side in the drawing. The coupling member 35 is coupled to the fork portion of the shaft 34 of the actuator 10 at the right end portion in the figure. The coupling member 35 and the fork portion of the shaft 34 are coupled by clearance fitting.

  In addition, a stopper lever 36 for restricting the valve opening degree when the valve is fully closed is attached in the vicinity of the fork portion of the pin rod 9. An annular plate-like collar 37 is mounted on the right side wall portion of the polygonal cylinder portion 6 on the right end side of the intake manifold 5 in the figure so that the stopper lever 36 does not slide directly on the intake manifold 5. The collar 37 is formed of a resin-based composite material (resin material) mixed or added with a low sliding resistance material (for example, a fluororesin). Thereby, since the drive resistance of the pin rod 9 when the stopper lever 36 slides directly on the intake manifold 5 can be reduced, the electric motor can be downsized.

  The stopper lever 36 is on one side (in the direction of the rotation axis) of a range (a range in which a plurality of valve holding portions to be described later is formed) fitting and holding a valve shaft provided for each of the plurality of intake flow control valves 1 to 4. It is held and fixed to the outer diameter part of the shaft on the actuator side. The stopper lever 36 is fully closed by being locked to a fully closed stopper member (fully closed stopper screw) 38 when all the intake flow control valves 1 to 4 are closed to the fully closed position (when the valve is fully closed). When the stopper portion (stopper portion) 36a and all the intake flow control valves 1 to 4 are opened to the fully open position (when the valve is fully open), the fully open stopper portion 36b is engaged with the fully open stopper member (fully open stopper screw) 39. have.

  The fully closed stopper member 38 is fastened and fixed with a nut 92 to a collar (fully closed stopper) 91 insert-molded in the cylindrical portion 30 of the intake manifold 5. The fully open stopper member 39 is fastened and fixed to a collar (full open stopper) 93 insert-molded in the cylindrical portion 30 using a nut 94. Thus, all the intake flow control valves 1 to 4 are configured such that when the fully closed stopper portion 36a of the stopper lever 36 is locked to the fully closed stopper member 38, all the valve opening degrees become the fully closed opening degrees. Be regulated. Further, all the intake flow control valves 1 to 4 are regulated so that all the valve opening degrees are fully opened when the fully opening stopper portion 36 b of the stopper lever 36 is locked to the fully opening stopper member 39.

  The valve drive device, particularly the electric motor, is configured to be energized and controlled by an engine control unit (hereinafter referred to as ECU). The ECU sets the fully closed position where the intake flow control valves 1 to 4 are fully closed as the fully closed position, and the fully open position where all the intake flow control valves 1 to 4 are fully opened as the fully open position. When the engine operating state (for example, engine speed, throttle opening, accelerator opening, target intake air amount, etc.) is variably controlled, the supply power to the electric motor is variably controlled. 4, the valve positions (valve opening degrees) of all intake flow control valves 1 to 4 can be controlled over the entire valve operating range from the fully closed position through the intermediate position to the fully open position.

  Here, the fully closed positions of all the intake flow control valves 1 to 4 are the smallest gaps between the intake flow control valves 1 to 4 and the passage wall surface of the housing 7, that is, the intake air flowing through the plurality of intake passages 12. This is the valve position (valve opening) at which the flow rate (intake amount) is minimized. In addition, the fully open position of the intake flow control valves 1 to 4 means that the clearance between the intake flow control valves 1 to 4 and the passage wall surface of the housing 7 is the maximum, that is, the intake air flow rate (intake amount) flowing through the plurality of intake passages 12. ) Is the maximum valve position (valve opening).

  Here, a backlash spring 41 is disposed on the other end side of the pin rod 9 in the rotation axis direction (opposite to the actuator side). The backlash spring 41 is configured to apply a spring load that biases the pin rod 9 toward the side that reduces the fitting gap formed at the coupling portion between the shaft 34 and the coupling member 35 of the actuator 10. Has been. The backlash spring 41 urges the relative rotation angle of the two first and second cylindrical sleeves 42 fitted to the outer periphery of the pin rod 9 to always be a constant angle (an angle corresponding to the fitting gap). . Further, the backlash spring 41 is accommodated in a spring accommodating space between a sleeve-shaped cylindrical portion 43 and a cap 44 that are integrally provided on the left side wall portion of the polygonal cylindrical portion 6 of the intake manifold 5. .

  Here, the plurality of valve units have polygonal holes (hereinafter referred to as square holes) 45 penetrating in the direction of the rotation axis of the pin rod 9 for each of the plurality of intake flow control valves 1 to 4. Each of the intake flow control valves 1 to 4 has a cylindrical valve fitting portion (hereinafter referred to as a valve shaft) 46 disposed so as to surround the square hole 45, and a rotational axis direction from the valve shaft 46. A plate-like valve body (valve body) and the like extended toward one side (one side) in the radial direction perpendicular to. Each square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 has a rotation axis direction perpendicular to the axial direction (intake flow direction) of each intake passage 12 formed for each of the plurality of housings 7. The through hole extends straight and is formed so as to penetrate each valve shaft 46 provided for each of the plurality of intake flow control valves 1 to 4 in the direction of the rotation axis.

  Here, the pin rod 9 of the present embodiment is a polygonal section shaft (square steel shaft) whose section perpendicular to the rotation axis direction is formed in a polygonal shape (for example, a quadrangular shape) using, for example, an iron-based metal material. The pin rod 9 is inserted into each square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 so that each valve shaft 46 provided for each of the plurality of intake flow control valves 1 to 4 has a predetermined shape. It has a plurality of fitting parts (hereinafter referred to as valve holding parts) 51 to 54 for holding at a valve mounting angle. Each square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 has a polygonal hole shape (square hole shape) corresponding to the cross-sectional shape (square shape) of the pin rod 9, that is, the valve holding of the pin rod 9. The holes 51 are formed in substantially the same hole shape as the cross-sectional shapes of the portions 51 to 54, and relative rotation between the intake flow control valves 1 to 4 and the pin rod 9 is restricted.

  The plurality of intake flow control valves 1 to 4 are all made of resin, and are integrally formed (resin integrated molding) into a predetermined shape by a resin material (for example, a glass fiber reinforced thermoplastic resin). The plurality of intake flow control valves 1 to 4 have a rotation center axis in a direction orthogonal to the axial direction (intake flow direction) of each housing 7 so as to be skewered into one pin rod 9. It is a combined rotary valve. The plurality of intake air flow control valves 1 to 4 are configured so that the flow rate of the intake air flowing through each intake passage 12 is minimized from the fully open position where the flow rate of the intake air flowing through each intake passage 12 is maximum. Each intake passage 12 for each of the plurality of housings 7 is opened and closed by changing the rotation angle (valve opening) in the valve operation range up to the closed position.

  Each of the valve bodies of the plurality of intake flow control valves 1 to 4 has a substantially rectangular shape surrounded by four sides composed of two pairs of opposite sides, and left and right sides (left and right side surfaces, The upper and lower sides (upper and lower end surfaces, both end surfaces) located on both ends in the vertical direction in the figure are longer (or shorter) than the both side surfaces. The plurality of intake flow control valves 1 to 4 are accommodated in each intake passage 12 formed for each of the plurality of housings 7 so as to be freely opened and closed (rotatable). The four corners (corner portions) of each of the valve bodies of the plurality of intake flow control valves 1 to 4 are formed in a right angle, but the four corners (corner portions) of each valve body are arcuate. Alternatively, R-shaped chamfering may be performed.

  The plurality of intake flow control valves 1 to 4 are each cut off a part (central portion) of the valve upper edge (the valve upper surface facing the passage wall surface of the housing upper wall 21 of the housing 7) of each valve body. By lacking, a rectangular main opening (notch, slit) 47 is formed for generating an intake vortex (tumble flow) in the intake air supplied into the combustion chamber of each cylinder of the engine. In addition, the plurality of intake flow control valves 1 to 4 have sub-openings (notches, slits) 48 having an opening area smaller than that of the main opening 47 by notching part of the left and right side surfaces of each valve body. Are formed. In addition, a plurality of valve surfaces on the back surface side of the front and back surfaces of the valve bodies of the intake flow control valves 1 to 4 have a plurality of heights so that the height gradually decreases from the valve shaft 46 toward the front end side of the valve body. Reinforcing ribs 49 are formed.

  Here, each valve shaft 46 formed for each of the plurality of intake flow control valves 1 to 4 is formed in a cylindrical shape so as to surround the periphery of the valve holding portions 51 to 54 of the pin rod 9 in the circumferential direction. Further, both end portions in the axial direction of the valve shaft 46 are provided with two valve sliding portions (valve sliding surfaces) that are slidably supported on the inner circumferences of the plurality of housings 7 via two bearings 26 and 27. ).

  In addition, each valve shaft 46 is offset from the center wall of each intake passage 12 on the bottom wall side, and is upstream of the center of each intake passage 12 in the intake flow direction in the intake flow direction. Is offset. That is, each valve shaft 46 is disposed near the opening end on the upstream side of each housing 7 and close to the bottom wall surface (lower surface) of the housing lower wall portion 22 of each housing 7. Therefore, the plurality of intake flow control valves 1 to 4 are in a state where the valve openings of all the intake flow control valves 1 to 4 are opened at the fully opened position (a state of the fully opened opening) (when the valves are fully opened). Further, the valve surface on the back surface side (the side where the reinforcing rib 49 is formed) of each valve body formed for each of the plurality of intake flow control valves 1 to 4 is the bottom wall surface of the housing lower wall portion 22 of each housing 7. Are arranged to face each other with a necessary minimum gap therebetween.

  The plurality of intake flow control valves 1 to 4 are in a state where all the intake flow control valves 1 to 4 are fully closed at the fully closed position (a state of the fully closed opening) (valve fully closed). Each valve shaft 46 formed for each of the plurality of intake flow control valves 1 to 4 is at a position biased to one side (lower side in the drawing) in the valve surface direction perpendicular to the plate thickness direction of each valve body. Be placed. Therefore, the plurality of intake flow control valves 1 to 4 constitute a cantilever valve having a valve shaft 46 that forms a rotation center on the opposite side to the free end side.

  The pin rod 9 is inserted into each square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 by press-fitting and skews the valve shafts 46 of the plurality of intake flow control valves 1 to 4. It is one drive shaft that connects all the intake flow control valves 1 to 4 so as to be interlocked with each other. The pin rod 9 is a polygonal cross-section shaft that extends straight in the direction of the rotation axis, and the valve holders 51 to 51 are press-fitted and fixed to the inner periphery of each valve shaft 46 provided for each of the plurality of intake flow control valves 1 to 4. 54. These valve holding portions 51 to 54 are provided corresponding to the intake flow control valves 1 to 4 for each of the plurality of valve units.

  That is, the valve holding portion 51 is a first fitting portion that is press-fitted and fixed to the inner periphery of the valve shaft 46 of the intake flow control valve 1, and the intake flow control valve 1 is set at a predetermined valve mounting angle (θv1). Mating and holding. The valve holding portion 52 is a second fitting portion that is press-fitted and fixed to the inner periphery of the valve shaft 46 of the intake flow control valve 2. The intake flow control valve 2 is set at a predetermined valve mounting angle (θv2). Mating and holding. The valve holding portion 53 is a third fitting portion that is press-fitted and fixed to the inner periphery of the valve shaft 46 of the intake flow control valve 3, and the intake flow control valve 3 is set at a predetermined valve mounting angle (θv3). Mating and holding. The valve holding portion 54 is a fourth fitting portion that is press-fitted and fixed to the inner periphery of the valve shaft 46 of the intake flow control valve 4. The intake flow control valve 4 is set at a predetermined valve mounting angle (θv4). Mating and holding.

  Here, in the intake vortex generator of the present embodiment, the valve opening between the cylinders of the engine when the valves are fully closed, with all the intake flow control valves 1 to 4 being fully closed, without increasing the rigidity of the pin rod 9 itself. For the purpose of absorbing variation in (fully closed opening), the valve mounting angle of each intake flow control valve 1 to 4 corresponding to each valve holding part 51 to 54 of the pin rod 9 with respect to each valve holding part 51 to 54 (Θv) is applied to each intake flow control valve 1 to 4 when the valve is fully closed in the valve opening operation direction (the valve forward tilt direction) (load torque due to intake negative pressure or backlash spring 41 The angle is set to correspond to the load torque (spring load).

  For example, the valve mounting angle (θv) with respect to each of the valve holding portions 51 to 54 of the pin rod 9 is set so as to increase stepwise in order of increasing distance from the stopper lever 36. Thus, the initial valve opening according to the pin rod twist angle generated in each valve holding portion 51 to 54 of the pin rod 9 by the load torque due to the intake negative pressure or the load torque due to the spring load of the backlash canceling spring 41 is previously set to the stopper. The distance from the lever 36 is set so as to increase stepwise in order of increasing distance.

Specifically, as shown in FIG. 1, for each valve shaft 46 provided for each of the plurality of intake flow control valves 1 to 4, each square hole 45 formed corresponding to each valve shaft 46. The set angle (θv) is set so as to increase stepwise from the shortest distance from the stopper lever 36. Thus, the set angles of the respective square holes 45 are provided for each of the plurality of intake flow control valves 1 to 4. A pin rod 9 is inserted into each valve shaft 46 to be provided.
That is, the set angle of the square hole 45 of the intake flow control valve 1 with respect to the valve shaft 46 of the intake flow control valve 1 is θv1, and the square hole of the intake flow control valve 2 with respect to the valve shaft 46 of the intake flow control valve 2 The setting angle of 45 is θv2, the setting angle of the square hole 45 of the intake flow control valve 3 with respect to the valve shaft 46 of the intake flow control valve 3 is θv3, and the intake flow with respect to the valve shaft 46 of the intake flow control valve 4 is When the set angle of the square hole 45 of the control valve 4 is θv4, the set angle (θv) of each square hole 45 is set so as to satisfy the relationship of θv1 <θv2 <θv3 <θv4.

Here, when the square hole (polygonal press-fit hole into which the pin rod 9 is press-fitted and fixed) 45 formed for each of the plurality of intake flow control valves 1 to 4 is 4 mm square, the intake air that is farthest from the stopper lever 36 is used. When the set angle (θv1) of the square hole 45 of the flow control valve 1 is the reference angle Adeg, the set angle (θv2) of the square hole 45 of the intake flow control valve 2 that is the second most distant from the stopper lever 36 is ( A + α) deg. Further, the set angle (θv3) of the square hole 45 of the intake flow control valve 3 having the second closest distance from the stopper lever 36 is (A + 2α) deg. Further, the set angle (θv4) of the square hole 45 of the intake air flow control valve 4 that is closest to the stopper lever 36 is (A + 3α) deg. Here, α is 2 deg. The value of α varies depending on the distance from the stopper lever 36 to the center position of the intake flow control valves 1 to 4 in the rotation axis direction, and also varies depending on the size of the square hole.
In the case of this embodiment, the surface direction of the hole wall surface of the square hole 45 and the extending direction of the valve body from the valve shaft 46 (valve surface (surface) direction) are relative to each of the intake flow control valves 1 to 4. Therefore, the square pipe having the square hole 45 is insert-molded inside each valve shaft 46 while changing the relative angle to each valve shaft 46 for each intake flow control valve 1 to 4. Anyway.

  Here, even if the pin rod 9 having a polygonal cross-sectional shape is directly supported in the bearing receiving holes 25 of the two valve bearing portions of the housing 7, the pin rod 9 cannot be smoothly rotated. Therefore, the pin rod 9 is covered with the valve shaft 46 of the intake flow control valves 1 to 4, and the outer peripheral side is connected to the two bearings 26 and 27 via both axial end portions (two valve sliding portions) of the valve shaft 46. It is pivotally supported. The thermoplastic resin used for the intake manifold 5, the housing 7, and the intake flow control valves 1 to 4 is polyamide resin (PA), unsaturated polyester resin (UP), polyphenylene sulfide from the viewpoint of heat resistance and strength. (PPS), polybutylene terephthalate (PBT) and the like are preferable.

Here, the intake flow control valves 1 to 4 are fully closed when the engine is cold or when the intake air amount may be small, that is, when the engine is started or during idling. That is, when the intake flow control valves 1 to 4 are fully closed at the fully closed position, a predetermined rotation angle (fully closed) in the valve opening operation direction with respect to a perpendicular perpendicular to the axial direction of the plurality of intake passages 12 is fully closed. The intake flow control valves 1 to 4 are arranged so as to be slightly inclined by an angle or an inclination angle).
Further, the intake flow control valves 1 to 4 are fully opened in the middle / high speed rotation region of the engine. That is, when the intake flow control valves 1 to 4 are fully opened at the fully open position, the intake flow is such that the two front and back surfaces (of the plate-like valve body) extend in substantially the same direction as the axial direction of the plurality of intake passages 12. Control valves 1 to 4 are arranged. When a large amount of intake air is required, that is, in the low-speed rotation region of the engine, the intake flow control valves 1 to 4 may be controlled so that the intermediate opening degree is half open from the fully closed position, that is, slightly opened. good.

[Operation of Example 1]
Next, the operation of the intake vortex generator (multiple integrated valve opening / closing device) of this embodiment will be briefly described with reference to FIGS.

  The ECU controls the power supplied to the electric motor (for example, energizes the electric motor) when the engine is warm and a large amount of intake air is required, that is, during normal operation of the engine. At this time, the intake flow control valves 1 to 4 are opened in the valve opening operation direction using the driving force of the electric motor. That is, control is performed so that the valve openings of all the intake flow control valves 1 to 4 are opened at the fully open position (state of the fully open opening).

  In this case, a plurality of intake air flows flowing from the plurality of intake passages 11 of the intake manifold 5 of the engine into the intake passages 12 formed for each of the plurality of housings 7 through the inlet portions of the respective housings 7 of the plurality of valve units, The intake passage 12 passes straight through and is introduced into the intake port 13 provided in the cylinder head 8 of the engine from the outlets of the plurality of housings 7. The intake air flow that has passed through the intake port 13 is supplied from the intake valve port of the intake port 13 into the combustion chamber. At this time, no vertical intake vortex flow (tumble flow) is generated in the combustion chamber.

  On the other hand, the ECU controls the power supplied to the electric motor (for example, energizes the electric motor) when the engine is cold and the intake air amount may be small, that is, when the engine is started or idling. At this time, the intake flow control valves 1 to 4 are closed in the valve closing operation direction by using the driving force of the electric motor. That is, control is performed so that the valve openings of all the intake flow control valves 1 to 4 are closed at the fully closed position (state of the fully closed opening).

  In this case, the intake air flow that flows into the plurality of intake passages 12 in the plurality of housings 7 from the plurality of intake passages 11 of the intake manifold 5 of the engine through the inlet portions of the plurality of housings 7 almost exclusively passes through the main opening 47. It passes through the outlet portions of the plurality of housings 7, is introduced into the upper layer portion of the intake port 13, and flows along the top wall surface of the upper layer portion of the intake port 13. Then, the intake flow that flows along the top wall of the upper layer portion of the intake port 13 is supplied from the intake valve port of the intake port 13 into the combustion chamber. 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

  Here, when the main opening 47 is formed at the upper end edge of each valve body of the plurality of intake flow control valves 1 to 4, a fuel pool (residual gasoline) is formed in the vicinity of the intake flow control valves 1 to 4. ) May occur, and if the accumulated fuel flows into the combustion chamber all at once due to factors such as vehicle inclination, there is a problem that incomplete combustion occurs.

  Therefore, at the time of engine start or idle operation, intake vortex flow is generated in the intake air supplied into the combustion chamber of each cylinder of the engine, and the combustion efficiency in the combustion chamber of each cylinder of the engine is improved to improve fuel efficiency, etc. In an intake vortex generator that can improve the engine, all intake flow control valves are used for the purpose of generating a tumble flow in the combustion chamber of each cylinder of the engine when the engine is cold and the intake air amount is small. 1 to 4 are set to a fully closed position that is closed at the fully closed position, that is, when the intake flow control valves 1 to 4 are fully closed, each of the plurality of intake flow control valves 1 to 4 is formed. Are formed for each of the plurality of intake flow control valves 1 to 4 so as to cancel not only the main intake flow passing through one main opening 47, but also part of the rewinding air flow of the main intake flow. Sub suction from four sub openings 48 Flow is fed into the intake ports 13. As a result, fuel accumulation in the vicinity of the intake flow control valves 1 to 4 is prevented.

Further, when the ignition switch is turned off (IG / OFF), the ECU controls the power supplied to the electric motor (for example, energizes the electric motor). As a result, all the intake flow control valves 1 to 4 are controlled so that they are slightly opened (slightly) in the valve opening operation direction from the fully closed position, that is, are in a state of intermediate opening that is half open. The ECU stops the power supplied to the electric motor when all the intake flow control valves 1 to 4 are set to the intermediate opening state.
At this time, the spring load of the backlash canceling spring 41 acts on the side (for example, the valve opening operation direction) that reduces the fitting gap formed at the coupling portion between the shaft 34 and the coupling member 35 of the actuator 10. All intake air flow control is performed by the gap between the tooth surfaces of the gear reduction mechanism motor gear and the intermediate reduction gear (backlash), or the gap between the tooth surfaces of the intermediate reduction gear and the final reduction gear (backlash). The valves 1 to 4 stop at a position inclined from the intermediate opening state (intermediate position) in the valve opening operation direction.

  Here, when a tumble flow is generated when a large amount of intake air is required in the low speed rotation region of the engine, the power supplied to the electric motor is controlled even when the engine is operating (for example, the electric motor is energized). And you may control so that the valve opening degree of all the intake flow control valves 1-4 may be in the state opened in the intermediate position (state of intermediate opening degree). In this case, a tumble flow is generated while increasing the intake air amount supplied into the combustion chamber for each cylinder of the engine to some extent. For this reason, the combustion efficiency in the combustion chamber in the low-speed rotation region of the engine is improved, and the fuel consumption, emission (for example, HC reduction effect) and the like are improved.

[Features of Example 1]
Here, in the intake vortex generator, as shown in FIGS. 2 and 4, during the operation of the engine, when all intake flow control valves 1 to 4 are fully closed (valves) When the intake negative pressure acts on the back surface of the valve body of each intake flow control valve 1 to 4 when fully closed), the valve opening operation direction around the valve shaft 46 of each intake flow control valve 1 to 4 (in FIG. 2) Load torque (bending moment) in the direction of the arrow is applied. As a result, twisting corresponding to the magnitude of the load torque occurs in each valve holding portion 51 to 54 that holds and fixes the valve shaft 46 of each intake flow control valve 1 to 4 in the pin rod 9. The twist of the valve holding portions 51 to 54 of the pin rod 9 appears more prominently in the case of a cantilever valve as in this embodiment.

  Further, as in this embodiment, the coupling portion between the shaft 34 of the actuator 10 and the coupling member 35 with respect to the pin rod 9 on the other end side in the rotation axis direction of the pin rod 9 (opposite to the actuator side). In the case where the backlash spring 41 for applying a spring load that biases the fitting gap formed on the side is reduced, if the spring load of the backlash spring 41 is applied to the pin rod 9, each intake air Load torque (bending moment) is applied in the valve opening operation direction around the valve shaft 46 of the flow control valves 1 to 4. Thereby, the pin rod 9 is twisted corresponding to the magnitude of the load torque.

  Here, when the valve is fully closed, the valve rods 51 to 54 of the pin rod 9 have different twist angles depending on the load torque that the pin rod 9 acts on the valve bodies of the intake flow control valves 1 to 4 in the valve opening operation direction. Is twisted, a deviation occurs in the fully closed opening degree of each of the intake flow control valves 1 to 4. That is, since the fully closed opening degree of the intake flow control valves 1 to 4 varies between the cylinders of the engine, the strength of the main intake flow that passes through the main openings 47 of the intake flow control valves 1 to 4 between the cylinders of the engine. The leak air flow rate when the valve is fully closed differs between the cylinders of the engine.

  Here, the twist angle of each of the valve holding portions 51 to 54 of the pin rod 9 increases stepwise in order of increasing distance from the stopper lever 36 that regulates the fully closed opening degree when the valve is fully closed. That is, when the fully closed opening degree of the intake flow control valve 4 closest to the stopper lever 36 is set as the reference opening degree, the intake flow control valves 1 to 3 are fully closed and opened as the distance from the stopper lever 36 increases. The degree is greatly advanced compared to the reference opening (inclined in the valve opening operation direction). For this reason, as the distance from the stopper lever 36 increases, the opening area of the main opening 47 when the valve is fully closed increases. Therefore, as the distance from the stopper lever 36 increases, the main flow of the intake flow control valves 1 to 4 increases. The strength of the main intake air flow passing through the opening 47 is weakened.

  Further, as the distance from the stopper lever 36 increases, the distance between the upper end surface (valve upper end surface) of the valve body of each intake flow control valve 1 to 4 and the passage wall surface of the housing upper wall portion 21 of each housing 7 increases. Since the gap becomes large, the leakage air flow rate when the valve is fully closed increases. Therefore, there arises a problem that fuel efficiency and emission are improved by improving combustion efficiency (HC reduction effect), that is, engine performance is lowered, which is an effect when an intake vortex generator is installed in an intake duct of an engine.

  Therefore, in the intake vortex generator (multiple integrated valve opening / closing device) of the present embodiment, each valve holding portion 51 of each intake flow control valve 1 to 4 corresponding to each valve holding portion 51 to 54 of the pin rod 9. The valve mounting angle (θv) with respect to ˜54 is set so as to increase stepwise in order of increasing distance from the stopper lever 36. Specifically, as shown in FIG. 1, for each valve shaft 46 provided for each of the plurality of intake flow control valves 1 to 4, each square hole 45 formed corresponding to each valve shaft 46. The set angle (θv) is set so as to increase stepwise in order of increasing distance from the stopper lever 36.

  Thus, the initial valve opening according to the pin rod twist angle generated in each valve holding portion 51 to 54 of the pin rod 9 by the load torque due to the intake negative pressure or the load torque due to the spring load of the backlash canceling spring 41 is previously set to the stopper. The distance from the lever 36 is set so as to increase stepwise in order of increasing distance. Therefore, even when a load torque in a different valve opening operation direction is applied to each intake flow control valve 1 to 4 arranged corresponding to each cylinder of the engine, the valve is fully closed. The valve openings of all the intake flow control valves 1 to 4 are set to be substantially the same valve opening.

As a result, it is possible to absorb variations in the valve opening between the cylinders of the engine when the valve is fully closed without increasing the rigidity of the pin rod 9 itself. Therefore, it is possible to suppress the difference in the strength of the main intake flow that passes through the main openings 47 of the intake flow control valves 1 to 4 among the cylinders of the engine. In addition, since the leakage air flow rate when the valve is fully closed between the engine cylinders can be suppressed, deterioration of the engine performance is prevented without increasing the size of the pin rod 9 (and the valve shaft 46) and increasing the cost. can do.
That is, since it is not necessary to increase the rigidity of the pin rod 9 itself, the outer diameter of the pin rod 9 does not increase, and the diameter of each square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 increases. An increase in the size of each valve shaft 46 disposed so as to surround the square hole 45 can be prevented. Accordingly, the cost can be reduced.
Further, since the weight of the plurality of intake flow control valves 1 to 4 and the pin rod 9 does not increase, the vibration resistance of the plurality of intake flow control valves 1 to 4 does not decrease. For this reason, even if vehicle vibration, engine vibration, or intake pulsation vibration pressure in the intake duct of the engine is transmitted to the intake manifold 5 (or the housing 7), the plurality of intake flow control valves 1 to 4 do not rattle. The intake flow control valves 1 to 4 and the housings 7 do not wear abnormally.

  FIG. 7 shows Example 2 of the present invention, and is a diagram showing the angle of the pin rod insertion surface with respect to the square hole.

  The pin rod 9 of the present embodiment has a plurality of valve holding portions 51 to 54 whose cross section perpendicular to the rotation axis direction is formed in a polygonal shape (for example, a quadrangular shape). A connecting portion 55 that connects the two valve holding portions 51 and 52 is provided between the two adjacent valve holding portions 51 and 52. Further, a connecting portion 56 for connecting the two valve holding portions 52 and 53 is provided between the two adjacent valve holding portions 52 and 53. A connecting portion 57 for connecting the two valve holding portions 53 and 54 is provided between the two adjacent valve holding portions 53 and 54. These connection parts 55-57 are inserted so that the inside of each shaft through-hole 15 formed for every polygonal cylinder part 6 (both side walls, partition wall) of the intake manifold 5 may penetrate in the rotation axis direction. . Moreover, the outer diameter of the connection parts 55-57 is smaller than the some valve | bulb holding parts 51-54.

In the intake vortex generator of the present embodiment, the valve opening between the cylinders of the engine (fully closed) when the valves fully closing all the intake flow control valves 1 to 4 are fully closed without increasing the rigidity of the pin rod 9 itself. For the purpose of absorbing variation in the opening degree, the valve mounting angle of each intake flow control valve 1 to 4 corresponding to each valve holding part 51 to 54 of the pin rod 9 with respect to each valve holding part 51 to 54 of the pin rod 9 (Θv) is applied to each intake flow control valve 1 to 4 when the valve is fully closed in the valve opening operation direction (the valve forward tilt direction) (load torque due to intake negative pressure or backlash spring 41 The angle is set to correspond to the load torque (spring load). For example, the valve mounting angle (θv) with respect to each valve holding portion 51 to 54 of the pin rod 9 is set in ascending order of the distance from the stopper lever 36 (see FIGS. 3 to 6) assembled on the right side of the pin rod 9 in the rotational axis direction. It is set to increase gradually.
Thereby, the valve opening degree of all the intake flow control valves 1 to 4 when the valve is fully closed is set to be substantially the same valve opening degree.

Specifically, as shown in FIG. 7, the pin rod insertion surface of each valve holding portion 51 to 54 that is inserted into each square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 by press fitting or the like. , That is, the angle (θs) of the pin rod insertion surface of each valve holding portion 51 to 54 with respect to the hole wall surface of each square hole 45 is set so as to increase stepwise in order of increasing distance from the stopper lever 36. In this way, the pin rods 9 having different angles of the pin rod insertion surfaces of the valve holding portions 51 to 54 are inserted into the square holes 45 formed for the plurality of intake flow control valves 1 to 4.
That is, the angle of the pin rod insertion surface of the valve holding part 51 with respect to the hole wall surface of the square hole 45 of the intake flow control valve 1 is θs1, and the pin rod insertion surface of the valve holding part 52 with respect to the hole wall surface of the square hole 45 of the intake flow control valve 2 Is the angle θs2, and the angle of the pin rod insertion surface of the valve holding portion 53 with respect to the hole wall surface of the square hole 45 of the intake flow control valve 3 is θs3, and the valve holding portion 54 with respect to the hole wall surface of the square hole 45 of the intake flow control valve 4 is When the angle of the pin rod insertion surface is θs4, the angle (θs) of the pin rod insertion surface of each valve holding part 51 to 54 is set so as to satisfy the relationship of θs1 <θs2 <θs3 <θs4.

  Here, when the square hole (polygonal press-fitting hole into which the pin rod 9 is press-fitted and fixed) 45 formed for each of the plurality of intake flow control valves 1 to 4 is 4 mm square, the valve having the longest distance from the stopper lever 36 is used. When the angle (θs1) of the pin rod insertion surface of the holding portion 51 is the reference angle Adeg, the angle (θs2) of the pin rod insertion surface of the valve holding portion 52 that is the second most distant from the stopper lever 36 is (A + α) deg. Become. Further, the angle (θs3) of the pin rod insertion surface of the valve holding portion 53 having the second closest distance from the stopper lever 36 is (A + 2α) deg. Further, the angle (θs4) of the pin rod insertion surface of the valve holding portion 54 with the closest distance from the stopper lever 36 is (A + 3α) deg. Here, α is 2 deg. The value of α varies depending on the distance from the stopper lever 36 to the center position in the direction of the rotation axis of each intake flow control valve 1 to 4, and the size of the square hole 45 and the physique of each valve holding portion 51 to 54 (outside It depends on the diameter. Therefore, the same effect as in the first embodiment can be achieved.

  FIG. 8 shows a third embodiment of the present invention and shows a valve unit.

  Each valve body provided for each of the intake flow control valves 1 to 4 of the present embodiment is provided with a pin rod peripheral portion 61 located in the vicinity of the valve shaft 46. A plurality of reinforcing ribs 62 extending from the valve shaft 46 toward the pin rod peripheral portion 61 of the valve body are formed on the back surface side of the valve body of the intake flow control valves 1 to 4. In this embodiment, the pin rod peripheral portion 61 and the reinforcing rib 62 formed on the back surface side of the pin rod peripheral portion 61 constitute a valve thick portion 63 that is thicker than the valve upper end edge of each valve body. ing. The reinforcing ribs 62 formed on the back surface side of the pin rod peripheral portion 61 have substantially the same height.

In the intake vortex generator of the present embodiment, the valve opening between the cylinders of the engine (fully closed) when the valves fully closing all the intake flow control valves 1 to 4 are fully closed without increasing the rigidity of the pin rod 9 itself. The rigidity of each pin rod peripheral portion 61 provided for each of the plurality of intake flow control valves 1 to 4 with respect to each intake flow control valve 1 to 4 when fully closed The rigidity is set so as to correspond to load torque (load torque due to intake negative pressure or load torque due to the spring load of the backlash spring 41) acting in the valve opening operation direction (the valve forward tilt direction). For example, the rigidity of the valve thick portion 63 provided for each valve body of the plurality of intake flow control valves 1 to 4 is set to the stopper lever 36 (see FIGS. 3 to 6) assembled to the right side of the pin rod 9 in the rotational axis direction. The distance is set so as to decrease step by step in ascending order.
Thereby, the valve opening degree of all the intake flow control valves 1 to 4 when the valve is fully closed is set to be substantially the same valve opening degree.

Specifically, as shown in FIG. 8, the plate thickness (valve thickness: Tv) of the valve thick portion 63 provided for each valve body of the plurality of intake flow control valves 1 to 4 is set to the stopper lever 36. The pin rod 9 is set in the square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 in which the valve wall thickness of the valve wall 63 is different. Is inserted.
That is, the valve thickness of the valve thickness portion 63 of the intake flow control valve 1 that is the farthest from the stopper lever 36 is Tv1, and the valve thickness of the intake flow control valve 2 that is the second most distant from the stopper lever 36. The valve thickness of the portion 63 is Tv2, the valve thickness of the valve thickness portion 63 of the intake flow control valve 3 that is the second closest to the stopper lever 36 is Tv3, and the distance from the stopper lever 36 is the closest. When the valve thickness of the valve thickness portion 63 of the flow control valve 4 is Tv4, each valve body of the plurality of intake flow control valves 1 to 4 is satisfied so that the relationship of Tv1>Tv2>Tv3> Tv4 is satisfied. The valve thickness (Tv) of the provided valve thickness portion 63 is set.

  As a result, even when load torques in different valve opening operation directions are applied to the respective intake flow control valves 1 to 4 arranged corresponding to the respective cylinders of the engine, a plurality of intake air flows. Corresponding to the magnitude of the load torque acting on each valve body of the control valves 1 to 4, the rigidity of the pin rod peripheral part 61 (particularly the valve thick part 63) of each valve body becomes high, and each valve holding part of the pin rod 9. Since the twist angle for each of 51 to 54 is substantially the same in all the valve holding portions 51 to 54, the valve openings of all the intake flow control valves 1 to 4 when the valves are fully closed are substantially the same as the valve openings. Is set to be Therefore, the same effect as in the first embodiment can be achieved.

  9 and 10 show a fourth embodiment of the present invention and show a valve unit.

  In the intake vortex generator of the present embodiment, the valve opening between the cylinders of the engine (fully closed) when the valves fully closing all the intake flow control valves 1 to 4 are fully closed without increasing the rigidity of the pin rod 9 itself. For the purpose of absorbing the variation in the opening degree, the valve upper edge of each valve body of the plurality of intake flow control valves 1 to 4 (the valve upper surface facing the passage wall surface of the housing upper wall portion 21 of the housing 7). The opening area of each of the main openings 47 formed in the valve is set to a load torque (depending on the intake negative pressure) that acts on each intake flow control valve 1 to 4 in the valve opening operation direction (the valve forward tilt direction) when the valve is fully closed. The opening area corresponding to the load torque and the load torque due to the spring load of the backlash spring 41) is set.

For example, the opening area of each main opening 47 formed for each valve body of the plurality of intake flow control valves 1 to 4 is set to the stopper lever 36 (FIGS. 3 to 6) assembled to the right side of the pin rod 9 in the rotational axis direction. It is set so as to increase stepwise in order of increasing distance from (see).
Specifically, as shown in FIG. 9, the height of the main opening 47 (main opening height: Hv) formed for each valve body of the plurality of intake flow control valves 1 to 4 is set as a stopper. A pin rod is set in a square hole 45 formed for each of the plurality of intake flow control valves 1 to 4 having different heights of the main openings 47 in such a manner that the distance from the lever 36 increases stepwise. 9 is inserted.

  That is, the height of the main opening 47 of the intake flow control valve 1 that is the farthest from the stopper lever 36 is Hv1, and the height of the main opening 47 of the intake flow control valve 2 that is the second most distant from the stopper lever 36 is set. The height of the main opening 47 of the intake flow control valve 3 with the height Hv2 and the second closest distance from the stopper lever 36 is Hv3, and the main flow of the intake flow control valve 4 with the closest distance from the stopper lever 36 is Hv3. When the height of the opening 47 is Hv4, each main opening 47 formed for each valve body of the plurality of intake flow control valves 1 to 4 so as to satisfy the relationship of Hv1 <Hv2 <Hv3 <Hv4. The height (Hv) is set.

  As a result, even when a load torque in a different valve opening operation direction is applied to each of the intake flow control valves 1 to 4 arranged corresponding to each cylinder of the engine, the valve is fully closed. Since the valve openings of all the intake flow control valves 1 to 4 are set to be substantially the same valve opening, the main openings 47 of all the intake flow control valves 1 to 4 when the valves are fully closed. Are set to have substantially the same opening area. Therefore, the same effect as in the first embodiment can be achieved.

  FIG. 11 shows a fifth embodiment of the present invention and shows a valve unit.

The intake manifold 5 according to the present embodiment includes a plurality of polygonal tube portions 6 each having a fitting hole 14 formed therein, and is housed inside these polygonal tube portions 6, and each intake passage 12 is formed therein. It is the intake duct of the double pipe structure comprised with the some housing 7 (refer FIG. 3 and FIG. 4).
The plurality of housings 7 have a housing thick portion 72 that is thicker than the housing thin portions 71 on the upstream and downstream sides in the intake flow direction in the vicinity of the fully closed positions of the plurality of intake flow control valves 1 to 4. is doing. The housing thick portion 72 is integrally formed (resin integrated molding) on the housing upper wall portion (wall of the upper portion of the housing) 21 of each housing 7.

In addition, each housing thick portion 72 provided for each of the plurality of housings 7 has a reference line X parallel to an axial direction (intake flow direction) of the average flow of intake air flowing in each intake passage 12. Convex portions that project toward the direction of reducing the passage cross-sectional area of the intake passage 12 (the rotation center position side of the plurality of intake flow control valves 1 to 4, the valve shaft side of the intake flow control valves 1 to 4) (Projection) 73 is disposed.
In addition, each convex portion 73 provided for each of the plurality of housings 7 is a direction for reducing the opening area of the main opening 47 formed on the valve upper end surface of each valve body for each of the plurality of intake flow control valves 1 to 4. (So as to enter the inside of the main opening 47), the passage walls of the housing upper wall portions 21 of the plurality of housings 7 are partially disposed in the front-rear direction and the left-right direction.

Moreover, each convex part 73 has a top surface when the valve openings of all the intake flow control valves 1 to 4 are fully closed at the fully closed position (a state of the fully closed opening) (valve fully closed). ) Is used as a facing surface 74 that faces a valve upper end surface of each valve body provided for each of the plurality of intake flow control valves 1 to 4 with a predetermined gap therebetween.
Further, the opposed surface 74 formed for each of the plurality of convex portions 73 is, when the valve is fully closed, the upper end surface of each valve body for each of the plurality of intake flow control valves 1 to 4, particularly the plurality of intake flow control valves 1 to 4. Opposite the opening edge of the main opening 47 every four with a predetermined gap. Each opposing surface 74 is provided at a high position protruding in the direction of reducing the passage cross-sectional area of each intake passage 12 with respect to the upstream or downstream passage wall surface in the intake flow direction from this opposing surface 74. It has been. Here, each convex portion 73 provided for each of the plurality of thick housing portions 72 is provided with a tapered step surface on the upstream side or the downstream side in the intake flow direction with respect to each opposing surface 74.

  In the intake vortex generator of the present embodiment, the valve opening between the cylinders of the engine (fully closed) when the valves fully closing all the intake flow control valves 1 to 4 are fully closed without increasing the rigidity of the pin rod 9 itself. For the purpose of absorbing variations in the opening degree, the distance (the upper wall portion of the housing) between the rotation center position of each intake flow control valve 1 to 4 (the axis of each valve shaft 46) and the opposing surface 74 of each projection 73 21 (height: Hh) is applied to each intake flow control valve 1 to 4 in the valve opening operation direction (valve forward tilt direction) when the valve is fully closed (load torque due to intake negative pressure, The distance (height) corresponding to the load torque due to the spring load of the eraser spring 41 is set.

Here, the height (Hh) of the upper wall portion 21 of the housing is increased stepwise in order of increasing distance from the stopper lever 36 (see FIGS. 3 to 6) assembled on the right side of the pin rod 9 in the rotational axis direction. It is set as follows.
Specifically, as shown in FIG. 11, the height (Hh) of the housing upper wall portion 21 is set so as to increase stepwise in order of increasing distance from the stopper lever 36. The pin rod 9 is inserted into the square holes 45 of the intake flow control valves 1 to 4 that are accommodated in the housings 7 having different heights of the wall portions 21 so as to be freely opened and closed.

  That is, the height of the housing upper wall 21 that accommodates the intake flow control valve 1 that is the farthest from the stopper lever 36 so as to be freely opened and closed is Hh1, and the intake flow control valve 2 that is the second most distant from the stopper lever 36. Hh2 is the height of the upper wall portion 21 of the housing that can be freely opened and closed, and Hh3 is the height of the upper wall portion 21 of the housing that is capable of opening and closing the intake flow control valve 3 that is the second closest to the stopper lever 36. When the height of the housing upper wall 21 that accommodates the intake flow control valve 4 having the closest distance from the stopper lever 36 is openable, the relationship of Hh1 <Hh2 <Hh3 <Hh4 is satisfied. The height (Hh) of the housing upper wall portion 21 is set.

  As a result, even when a load torque in a different valve opening operation direction is applied to each of the intake flow control valves 1 to 4 arranged corresponding to each cylinder of the engine, the valve is fully closed. Are set so that the valve openings of all the intake flow control valves 1 to 4 are substantially the same. That is, a gap formed between each main opening 47 of the plurality of intake flow control valves 1 to 4 and each facing surface 74 of the housing upper wall portion 21 of the housing 7 when the valve is fully closed, that is, each main opening. Since the opening area of the portion 47 is set to be substantially the same opening area, the valve opening degrees of all the intake flow control valves 1 to 4 when the valves are fully closed are substantially the same valve opening degree. Is set. Therefore, the same effect as in the first embodiment can be achieved.

  FIG. 12 shows Embodiment 6 of the present invention, and FIGS. 12A and 12B show the main structure of the valve unit.

  In this embodiment, as shown in FIG. 12 (a), each valve body of each of the plurality of intake flow control valves 1 to 4 has a valve thickness portion that is thicker than the peripheral portion of the pin rod on the valve shaft side. 64. Each valve thick portion 64 formed for each of the plurality of intake flow control valves 1 to 4 separates a predetermined gap from the passage wall surface (opposing surface) of the housing upper wall portion 21 for each of the plurality of housings 7 when the valve is fully closed. Opposite valve upper end surfaces 65. Each valve thick portion 64 closes each intake flow control valve 1 to 4 from a reference line Y parallel to the valve surface direction in the pin rod peripheral portion of each valve body for each of the plurality of intake flow control valves 1 to 4. It has a convex part (projection part) 66 arranged in an arc shape so as to protrude toward the valve operating direction. Each convex portion 66 formed for each of the plurality of intake flow control valves 1 to 4 is a valve upper end edge of each of the plurality of intake flow control valves 1 to 4 (near the valve upper end surface on the opposite side to the valve shaft side). Are integrally formed (resin integrated molding).

  Here, a curved surface 67 that is curved along the rotation locus of the valve upper end surface 65 of the intake flow control valves 1 to 4 is formed on the convex portion 66 side in the valve upper end surface 65. In other words, the valve upper end surface 65 is separated from the passage wall surface of the housing upper wall portion 21 of the plurality of housings 7 by a predetermined gap over a range from the minimum value to the maximum value of the pin rod twist angle generated by the load torque, for example. Are used as opposing surfaces facing each other. Further, the valve surface on the front side of the two front and back surfaces of the valve bodies of the intake flow control valves 1 to 4 gradually increases in height from the topmost portion (top surface) 68 of the convex portion 66 toward the pin rod peripheral portion side. A plurality of reinforcing ribs 69 are formed so as to be low.

  In the intake vortex generator of the present embodiment, the valve opening between the cylinders of the engine (fully closed) when the valves fully closing all the intake flow control valves 1 to 4 are fully closed without increasing the rigidity of the pin rod 9 itself. For the purpose of absorbing variation in the opening degree, the amount of protrusion in the valve closing operation direction of each convex portion 66 formed for each of the plurality of intake flow control valves 1 to 4 is set to the intake flow control valve when the valve is fully closed. Maximum pin rod twist angle generated by load torque (load torque due to intake negative pressure or load torque due to spring load of backlash spring 41) acting in the valve opening operation direction (valve forward tilt direction) for every 1 to 4 The protrusion amount is set in accordance with the value (the twist angle of the valve holding portion 51 that holds the intake flow control valve 1 that is the farthest from the stopper lever 36).

  As a result, even when a load torque in a different valve opening operation direction is applied to each of the intake flow control valves 1 to 4 arranged corresponding to each cylinder of the engine, the valve is fully closed. Are set so that the valve openings of all the intake flow control valves 1 to 4 are substantially the same. That is, the fully closed opening degree of the intake flow control valve 4 that is closest to the stopper lever 36 (see FIGS. 3 to 6) assembled on the right side of the pin rod 9 in the rotational axis direction is δ1, and the distance from the stopper lever 36 is When the fully closed opening degree of the intake flow control valve 1 with the longest distance is δ2, δ1 = δ2. Thus, when the valve is fully closed, the valve upper end surface 65 of the plurality of intake flow control valves 1 to 4 and the curved surface 67 of each convex portion 66 and the passage wall surface of each housing upper wall portion 21 for each of the plurality of housings 7. Since the opening areas of the gaps formed between them are set to be substantially the same opening area, the valve opening degrees of all the intake flow control valves 1 to 4 when the valves are fully closed are substantially the same. Is set to be Therefore, the same effect as in the first embodiment can be achieved.

Further, as shown in FIG. 12B, the plurality of housings 7 are located closer to the fully closed positions of the plurality of intake flow control valves 1 to 4 than the thin housing portion 71 on the upstream side in the intake flow direction. A thick housing portion 72 is provided. The thin housing portion 71 and the thick housing portion 72 are integrally formed (resin integrated molding) on the housing upper wall portion (wall of the upper portion of the housing) 21 of each housing 7.
In addition, each housing thick portion 72 provided for each of the plurality of housings 7 has a reference line X parallel to an axial direction (intake flow direction) of the average flow of intake air flowing in each intake passage 12. Convex portions that project toward the direction of reducing the passage cross-sectional area of the intake passage 12 (the rotation center position side of the plurality of intake flow control valves 1 to 4, the valve shaft side of the intake flow control valves 1 to 4) (Projection) 75 is disposed.

Further, each projection 75 provided for each of the plurality of housing thick portions 72 reduces the opening area of the main opening 47 formed on the valve upper end surface of each valve body for each of the plurality of intake flow control valves 1 to 4. In the direction to be changed (so as to enter the inside of the main opening 47), the passage wall surfaces of the housing upper wall portions 21 of the plurality of housings 7 are partially disposed in the front-rear direction and the left-right direction.
Further, each of the thin housing portions 71 of the plurality of housings 7 and each convex portion 75 of each of the plurality of thick housing portions 72 has a passage wall surface in the vicinity of the fully closed position so that all the intake flow control valves 1 to 4 are opened. The valve upper end face of each valve body provided for each of the plurality of intake flow control valves 1 to 4 when the degree is fully closed at the fully closed position (when the valve is fully closed) (when the valve is fully closed) Are used as opposing surfaces 76 and 77 that face each other with a gap therebetween.

  Further, each opposing surface 76 formed for each of the plurality of thin housing portions 71 has a valve body of the intake flow control valve 4 that is at least the distance from the stopper lever 36 (see FIGS. 3 to 6) when the valve is fully closed. Are opposed to the upper end surface of the valve, in particular, the opening edge of the main opening 47 of the intake flow control valve 4 with a predetermined gap. Further, each facing surface 76 formed for each of the plurality of thin housing portions 71 is a flat surface (plane) extending straight from the facing surface 77 toward the upstream side in the intake flow direction.

  Further, the opposed surface 77 formed for each of the plurality of convex portions 75 is at least the valve upper end surface of the valve body of the intake flow control valve 1 that is the farthest from the stopper lever 36, particularly the main opening of the intake flow control valve 1. It faces the opening edge of 47 with a predetermined gap. In addition, each facing surface 77 formed for each of the plurality of convex portions 75 is provided on each of the intake flow control valves 1 to 4 with respect to a passage wall surface (facing surface 76) on the upstream side of the facing surface 77 in the intake flow direction. It is extended in the valve opening operation direction. Further, each facing surface 77 formed for each of the plurality of convex portions 75 is a curved surface curved in an arc shape so as to follow the rotation locus of the valve upper end surface of each valve body of each intake flow control valve 1 to 4. .

It should be noted that the distance from the upper end surface of the valve body of the intake flow control valve 2, the opening edge of the main opening 47 of the intake flow control valve 2, and the stopper lever 36 is the second most distant from the stopper lever 36. The upper end surface of the valve body of the intake flow control valve 3 that is the second closest, particularly the opening edge of the main opening 47 of the intake flow control valve 3, has a predetermined gap between the opposing surface 76 or the opposing surface 77. Facing each other.
Here, each of the opposing surfaces 76 and 77 formed for each of the plurality of housings 7 has a plurality of intake flow control valves 1 over a range from the minimum value to the maximum value of the pin rod twist angle generated by the load torque, for example. It is possible to oppose the valve | bulb upper end surface of each valve body of -4 with a predetermined clearance.

  In the intake vortex generator of the present embodiment, the valve opening between the cylinders of the engine (fully closed) when the valves fully closing all the intake flow control valves 1 to 4 are fully closed without increasing the rigidity of the pin rod 9 itself. For the purpose of absorbing variation in the opening degree, the length of the curved surface of each convex portion 75 formed for each of the plurality of housings 7 is opened for each intake flow control valve 1 to 4 when the valve is fully closed. The maximum value of the pin rod twist angle (the distance from the stopper lever 36) generated by the load torque (load torque due to intake negative pressure or load torque due to the spring load of the backlash spring 41) acting in the operating direction (valve forward tilt direction). The curved surface length is set corresponding to the twist angle of the valve holding portion 51 that holds the farthest intake flow control valve 1.

  As a result, even when a load torque in a different valve opening operation direction is applied to each of the intake flow control valves 1 to 4 arranged corresponding to each cylinder of the engine, the valve is fully closed. Are set so that the valve openings of all the intake flow control valves 1 to 4 are substantially the same. That is, the fully closed opening degree of the intake flow control valve 4 that is closest to the stopper lever 36 (see FIGS. 3 to 6) assembled on the right side of the pin rod 9 in the rotational axis direction is δ1, and the distance from the stopper lever 36 is When the fully closed opening degree of the intake flow control valve 1 with the longest distance is δ2, δ1 = δ2.

  Thereby, the opening area of the gap formed between the valve upper end surface of each valve body of the plurality of intake flow control valves 1 to 4 and the opposing surfaces 76 and 77 for each of the plurality of housings 7 when the valve is fully closed. However, the valve openings of all the intake flow control valves 1 to 4 when the valves are fully closed are set to have substantially the same valve opening. Therefore, the same effect as in the first embodiment can be achieved.

[Modification]
In this embodiment, the intake vortex generator is configured so as to be able to generate a vertical intake vortex (tumble flow) for promoting combustion of the air-fuel mixture in the combustion chamber of each cylinder of the engine. The intake vortex generator may be configured to be able to generate a lateral intake vortex (swirl) for promoting combustion of the air-fuel mixture in the combustion chamber of each cylinder of the engine. Further, the intake vortex generator may be configured to be able to generate a squish vortex for promoting engine combustion.

  In this embodiment, the multiple integrated valve opening / closing device of the present invention is applied to an intake flow control device (intake vortex flow generating device) for an internal combustion engine, but the multiple integrated valve opening / closing device of the present invention is applied to an internal combustion engine. The present invention may be applied to an intake air amount control device for an internal combustion engine that controls the flow rate of intake air taken into the combustion chamber of each cylinder of the engine. In this case, an intake air amount control valve such as an idle speed control valve or a throttle valve is incorporated in the housing.

  Further, the multiple integrated valve opening / closing device of the present invention may be applied to a variable intake device for an internal combustion engine provided with a variable intake valve. The variable intake valve is an intake control valve for an internal combustion engine that varies the passage length or the cross-sectional area of the intake passage of the intake manifold in accordance with the engine speed. The variable intake device for an internal combustion engine switches the intake passage by a variable intake valve so that the length of the intake passage of the intake manifold is extended, for example, when the engine speed is in a low / medium speed rotation region, and the engine speed is This is a device that can improve the engine output shaft torque (engine torque) regardless of the engine rotation speed by switching the intake passage with a variable intake valve so that the intake manifold passage length is shortened in the high speed rotation region. . Further, as the air, intake air (intake air), exhaust gas, or the like may be used.

  In the present embodiment, the valve drive device that drives the plurality of intake flow control valves 1 to 4 to close (or opens) includes an electric motor and a power transmission mechanism (for example, a gear reduction mechanism). Although it is composed of an electric actuator equipped with a power unit, a valve drive device that opens or closes a plurality of valves can be operated as a negative pressure actuated actuator or electromagnetic type equipped with an electromagnetic or electric negative pressure control valve. You may comprise by an actuator. A valve urging means such as a spring for urging a plurality of valves in the valve opening direction or the valve closing direction may be provided.

  In this embodiment, the multiple integrated valve opening / closing device of the present invention is mounted on the intake system (or exhaust system) of an in-line 4-cylinder engine in which cylinders are arranged in groups. The valve opening / closing device may be mounted on an intake system (or exhaust system) of an internal combustion engine having a plurality of banks in which cylinders are arranged in groups. Such internal combustion engines include multi-cylinder engines such as V-type engines, horizontal engines, and horizontally opposed engines. Further, the valve is not limited to a cantilever valve, and a double-sided valve may be used.

  Also, the electric motor is energized during normal operation of the engine, the intake flow control valves 1 to 4 are fully opened, the energization of the electric motor is stopped during engine start or idle operation, and the intake flow control valves 1 to 4 are A normally closed intake flow control valve that is fully closed may be employed. Further, the energization of the electric motor is stopped during normal operation of the engine, the intake flow control valves 1 to 4 are fully opened, the electric motor is energized during engine start-up or idle operation, and the intake flow control valves 1 to 4 are A normally-open intake flow control valve that is fully closed may be employed.

In the present embodiment, the front shape of the intake flow control valves 1 to 4 is substantially rectangular (rectangular), but the front shape of the intake flow control valves 1 to 4 is circular, elliptical, oval, or polygonal. It is also good. In this case, the shape of each intake passage 12 for each of the plurality of housings 7 is changed according to the front shape of the intake flow control valves 1 to 4.
Further, in this embodiment, a plurality of valve units in which one valve is incorporated in one housing so as to be freely opened and closed are arranged at regular intervals in the direction of the rotation axis of the pin rod 9 inside an intake manifold 5 as a casing. The multiple integral type valve opening and closing device is adopted, but a multiple integral type valve opening and closing device in which a plurality of valves are directly arranged at regular intervals in the rotation axis direction of the shaft inside the casing (intake duct or engine head cover). May be adopted. In this case, the housing 7 can be eliminated.

It is explanatory drawing which showed the setting angle of the square hole with respect to a valve shaft (Example 1). 1 is a cross-sectional view showing an intake air flow control device for an internal combustion engine (Example 1). BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an exploded perspective view showing an intake vortex generator (multiple integrated valve opening / closing device) (Example 1). FIG. 1 is a cross-sectional view showing an intake vortex generator (multiple integrated valve opening / closing device) (Example 1). (Example 1) which is ZZ sectional drawing of FIG. (Example 1) which is the stopper lever of a pin rod, and the coupling | bond part of the shaft and coupling member of an actuator. (A) is the side view which showed the pin rod, (b) is AA sectional drawing of (a), (c) is BB sectional drawing of (a) (Example 2). (Example 3) which is sectional drawing which showed the valve unit. (Example 4) which is sectional drawing which showed the valve unit. (Example 4) which is the perspective view which showed the valve unit. (Example 5) which is sectional drawing which showed the valve unit. (A), (b) is sectional drawing which showed the main structures of the valve unit (Example 6).

Explanation of symbols

1 Intake flow control valve (first valve, plate-like valve body, valve body)
2 Intake flow control valve (second valve, plate-like valve body, valve body)
3 Intake flow control valve (3rd valve, plate-like valve body, valve body)
4 Intake flow control valve (4th valve, plate-like valve body, valve body)
5 Intake manifold (casing)
6 Polygonal cylinder part of intake manifold (first cylinder part of casing)
7 Housing (second cylinder part of casing)
8 Engine cylinder head 9 Pin rod (shaft)
10 Actuator (Valve Drive Device)
11 Intake manifold intake passage (air passage)
12 Housing intake passage (air passage)
13 Cylinder head intake port 34 Actuator shaft (output shaft)
35 Coupling member 36 Stopper lever (stopper)
41 Backlash eraser 45 Inlet flow control valve square hole (through hole, polygonal hole)
46 Valve shaft of intake flow control valve 47 Main opening of intake flow control valve 48 Sub-opening of intake flow control valve 49 Reinforcing rib of intake flow control valve 51 Valve holding portion of pin rod (first fitting portion)
52 Pin rod valve holder (second fitting part)
53 Pin rod valve holder (third fitting)
54 Pin rod valve holder (fourth fitting part)
61 Inlet Flow Control Valve Pin Rod Periphery 62 Intake Flow Control Valve Reinforcement Rib 63 Inlet Flow Control Valve Valve Thickness 64 Inlet Flow Control Valve Thickness 65 Inlet Flow Control Valve Upper End Surface 66 Intake Flow Control Projection (protrusion) of the valve
67 Curved surface of convex part (opposite surface)
68 Topmost part of convex part (top face)
71 Housing thin part of housing 72 Housing thick part of housing 73 Convex part (projection part) of housing
74 Opposite surface of housing thick part (convex part) 75 Housing convex part (protrusion part)
76 Opposite surface of thin housing part 77 Opposite surface (curved surface) of thick housing part (convex part)
36a Stopper lever fully closed stopper (stopper)
36b Stopper lever fully open stopper

Claims (36)

(A) a casing having a plurality of air flow paths that are independently connected to each cylinder of the internal combustion engine; and (b) disposed corresponding to each of the plurality of air flow paths and penetrating in the direction of the rotation axis. A plurality of valves having through holes;
(C) one shaft that is disposed so as to penetrate each through-hole formed in each valve in the direction of the rotation axis, and that couples the plurality of valves so as to be skewered;
(D) In a multiple integrated valve opening and closing device comprising an actuator that generates a driving force for driving the plurality of valves in the valve opening operation direction or the valve closing operation direction via the shaft.
The shaft has a plurality of fitting portions for holding the plurality of valves at a predetermined mounting angle;
The mounting angle of each valve corresponding to each of the plurality of fitting portions with respect to each of the plurality of fitting portions is an angle corresponding to the load torque acting in the valve opening operation direction for each of the valves when the valve is fully closed. A multi-unit integrated valve opening and closing device characterized in that In the multiple integrated valve opening and closing device according to claim 1,
Each valve corresponding to each of the plurality of fitting portions has a cylindrical valve shaft disposed so as to surround the periphery of the through hole, and a radial direction perpendicular to the rotation axis direction from the valve shaft. A multi-unit integrated valve opening / closing device characterized by having a plate-like valve element extended. The multiple integrated valve opening and closing device according to claim 2,
Each valve corresponding to each of the plurality of fitting portions is a cantilever valve in which the valve shaft is biased to one side in the valve surface direction perpendicular to the plate thickness direction of the plate-like valve body. A multi-unit integrated valve opening and closing device. The multiple-integrated type valve opening / closing device according to claim 2 or 3,
Each plate-like valve element provided for each of the plurality of valves has intake air supplied to the cylinders of the internal combustion engine by cutting away an end surface opposite to each valve shaft provided for each of the plurality of valves. A multiple-integrated type valve opening / closing device having an opening for generating a vortex flow in the valve. The multiple-integrated valve opening / closing device according to any one of claims 1 to 4,
The mounting angle of each valve corresponding to each of the plurality of fitting portions with respect to each of the plurality of fitting portions is set so that the opening degrees of all the valves when the valves are fully closed are substantially the same valve opening degree. A multi-unit integrated valve opening and closing device characterized by that. The multiple-integrated valve opening and closing device according to any one of claims 1 to 5,
The shaft has a stopper portion that regulates a valve opening degree when the valve is fully closed on one side in a rotation axis direction from a range inserted into each through hole of each of the plurality of valves. Multi-unit integrated valve opening and closing device. The multiple integrated valve opening and closing device according to claim 6,
The mounting angle of each valve corresponding to each of the plurality of fitting portions with respect to each of the plurality of fitting portions is set so as to increase stepwise in order of increasing distance from the stopper portion. Multi-unit integrated valve opening and closing device. In the multiple integrated valve opening and closing device according to claim 6 or 7,
Each fitting portion provided on the shaft is formed in a polygonal cross-sectional shape,
Each of the through holes formed for each of the plurality of valves is formed in a polygonal hole shape corresponding to a cross-sectional shape of each of the fitting portions. The multiple integrated valve opening and closing device according to claim 8,
Each valve corresponding to each of the plurality of fitting portions has a cylindrical valve shaft so as to surround each of the through holes,
For each valve shaft provided for each of the plurality of valves, the set angle of each through hole formed corresponding to each valve shaft is increased stepwise in order of increasing distance from the stopper portion. A multi-unit integrated valve opening and closing device characterized by being set to. The multiple integrated valve opening and closing device according to claim 8,
The plurality of fitting portions are provided corresponding to the plurality of valves at regular intervals in the rotation axis direction of the shaft, and are inserted into the through holes formed for the plurality of valves. And
The angle of the insertion surface of each fitting portion to be inserted into each through hole is set so as to increase stepwise in order of increasing distance from the stopper portion. apparatus. (A) a casing having a plurality of air flow paths that are independently connected to each cylinder of the internal combustion engine; and (b) disposed corresponding to each of the plurality of air flow paths and penetrating in the direction of the rotation axis. A plurality of valves having through holes;
(C) one shaft that is disposed so as to penetrate each through-hole formed in each valve in the direction of the rotation axis, and that couples the plurality of valves so as to be skewered;
(D) In a multiple integrated valve opening and closing device comprising an actuator that generates a driving force for driving the plurality of valves in the valve opening operation direction or the valve closing operation direction via the shaft.
The shaft has a plurality of fitting portions for holding the plurality of valves at a predetermined mounting angle;
Each valve corresponding to each of the plurality of fitting portions has a cylindrical valve shaft disposed so as to surround the periphery of the through hole, and a radial direction perpendicular to the rotation axis direction from the valve shaft. A plate-shaped valve element extended,
The rigidity of each plate-like valve element provided for each of the plurality of valves is set so as to correspond to the load torque acting in the valve opening operation direction for each of the valves when the valve is fully closed. A multi-unit integrated valve opening and closing device. The multiple integrated valve opening and closing device according to claim 11,
Each valve corresponding to each of the plurality of fitting portions is a cantilever valve in which the valve shaft is biased to one side in the valve surface direction perpendicular to the plate thickness direction of the plate-like valve body. A multi-unit integrated valve opening and closing device. The multiple-integrated type valve opening / closing device according to claim 11 or 12,
Each plate-like valve element provided for each of the plurality of valves has intake air supplied to the cylinders of the internal combustion engine by cutting away an end surface opposite to each valve shaft provided for each of the plurality of valves. A multiple-integrated type valve opening / closing device having an opening for generating a vortex flow in the valve. The multiple-integrated valve opening and closing device according to any one of claims 11 to 13,
The shaft has a stopper portion that regulates a valve opening degree when the valve is fully closed on one side in a rotation axis direction from a range inserted into each through hole of each of the plurality of valves. Multi-unit integrated valve opening and closing device. The multiple integrated valve opening and closing device according to claim 14,
Each plate-like valve body has a thick portion of a predetermined plate thickness on each valve shaft side provided for each of the plurality of valves.
The plate thickness of each thick portion provided for each plate-like valve body is set so as to decrease stepwise in order of increasing distance from the stopper portion. apparatus. (A) a casing having a plurality of air flow paths that are independently connected to each cylinder of the internal combustion engine; and (b) disposed corresponding to each of the plurality of air flow paths and penetrating in the direction of the rotation axis. A plurality of valves having through holes;
(C) one shaft that is disposed so as to penetrate each through-hole formed in each valve in the direction of the rotation axis, and that couples the plurality of valves so as to be skewered;
(D) In a multiple integrated valve opening and closing device comprising an actuator that generates a driving force for driving the plurality of valves in the valve opening operation direction or the valve closing operation direction via the shaft.
The shaft has a plurality of fitting portions for holding the plurality of valves at a predetermined mounting angle;
Each valve corresponding to each of the plurality of fitting portions has a cylindrical valve shaft disposed so as to surround the periphery of the through hole, and a radial direction perpendicular to the rotation axis direction from the valve shaft. A plate-shaped valve element extended,
Each plate-like valve element provided for each of the plurality of valves has intake air supplied to the cylinders of the internal combustion engine by cutting away an end surface opposite to each valve shaft provided for each of the plurality of valves. Has an opening for creating a vortex flow,
The opening area of each opening formed for each plate-like valve body is set to be an opening area corresponding to the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. A multi-unit integrated valve opening and closing device characterized by that. The multiple integrated valve opening and closing device according to claim 16,
Each valve corresponding to each of the plurality of fitting portions is a cantilever valve in which the valve shaft is biased to one side in the valve surface direction perpendicular to the plate thickness direction of the plate-like valve body. A multi-unit integrated valve opening and closing device. The multiple-integrated type valve opening / closing device according to claim 16 or 17,
The shaft has a stopper portion that regulates a valve opening degree when the valve is fully closed on one side in a rotation axis direction from a range inserted into each through hole of each of the plurality of valves. Multi-unit integrated valve opening and closing device. The multiple integrated valve opening and closing device according to claim 18,
The opening / closing area of each opening formed for each plate-shaped valve element is set so as to increase stepwise in order of increasing distance from the stopper portion. apparatus. (A) a casing having a plurality of air passages independently connected to each cylinder of the internal combustion engine; and (b) disposed corresponding to each of the plurality of air passages and penetrating in the direction of the rotation axis. A plurality of valves having through holes;
(C) one shaft that is disposed so as to penetrate each through-hole formed in each valve in the direction of the rotation axis, and that couples the plurality of valves so as to be skewered;
(D) In a multiple integrated valve opening and closing device comprising an actuator that generates a driving force for driving the plurality of valves in the valve opening operation direction or the valve closing operation direction via the shaft.
The shaft has a plurality of fitting portions for holding the plurality of valves at a predetermined mounting angle;
Each valve corresponding to each of the plurality of fitting portions has a cylindrical valve shaft disposed so as to surround the periphery of the through hole, and a radial direction perpendicular to the rotation axis direction from the valve shaft. A plate-shaped valve element extended,
The casing has a plurality of cylindrical portions in which air flow paths are formed,
The plurality of cylindrical portions have a convex portion projecting in a direction of reducing a cross-sectional area of each air channel on a channel wall surface in the vicinity of the fully closed position of each valve,
Each convex portion provided for each of the plurality of cylindrical portions is used as an opposing surface whose top surface is opposed to an end surface of each plate-like valve body provided for each of the plurality of valves when the valve is fully closed,
The distance between the rotation center position of each valve and the position of the opposing surface of each projection is a distance corresponding to the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. A multi-unit integrated valve opening and closing device characterized by being set. The multiple-integrated valve opening and closing device according to claim 20,
Each valve corresponding to each of the plurality of fitting portions is a cantilever valve in which the valve shaft is biased to one side in the valve surface direction perpendicular to the plate thickness direction of the plate-like valve body. A multi-unit integrated valve opening and closing device. The multiple-integrated type valve opening / closing device according to claim 20 or 21,
Each plate-like valve element provided for each of the plurality of valves has intake air supplied to the cylinders of the internal combustion engine by cutting away an end surface opposite to each valve shaft provided for each of the plurality of valves. A multiple-integrated type valve opening / closing device having an opening for generating a vortex flow in the valve. The multiple-integrated valve opening and closing device according to any one of claims 20 to 22,
The shaft has a stopper portion that regulates a valve opening degree when the valve is fully closed on one side in a rotation axis direction from a range inserted into each through hole of each of the plurality of valves. Multi-unit integrated valve opening and closing device. The multiple integrated valve opening and closing device according to claim 23,
The distance between the rotation center position of each valve and the position of the opposing surface of each convex portion is set so as to increase stepwise in order of increasing distance from the stopper portion. Body valve opening and closing device. (A) a casing having a plurality of air flow paths that are independently connected to each cylinder of the internal combustion engine; and (b) disposed corresponding to each of the plurality of air flow paths and penetrating in the direction of the rotation axis. A plurality of valves having through holes;
(C) one shaft that is disposed so as to penetrate each through-hole formed in each valve in the direction of the rotation axis, and that couples the plurality of valves so as to be skewered;
(D) In a multiple integrated valve opening and closing device comprising an actuator that generates a driving force for driving the plurality of valves in the valve opening operation direction or the valve closing operation direction via the shaft.
The shaft has a plurality of fitting portions for holding the plurality of valves at a predetermined mounting angle;
Each valve corresponding to each of the plurality of fitting portions has a cylindrical valve shaft disposed so as to surround the periphery of the through hole, and a radial direction perpendicular to the rotation axis direction from the valve shaft. A plate-shaped valve element extended,
Each plate-like valve element provided for each of the plurality of valves is in the vicinity of the end surface opposite to each valve shaft side provided for each of the plurality of valves so as to follow the rotation trajectory of each of the plate-like valve elements. It has a protruding part curved in an arc shape,
Each protrusion provided for each plate-like valve body protrudes in the valve closing operation direction of each valve with respect to the valve surface on the valve shaft side from the protrusion,
The protrusion amount of each protrusion in the valve closing operation direction is a protrusion amount corresponding to the maximum value of the shaft twist angle generated by the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. A multi-unit integrated valve opening and closing device characterized by being set. The multiple integrated valve opening and closing device according to claim 25,
Each valve corresponding to each of the plurality of fitting portions is a cantilever valve in which the valve shaft is biased to one side in the valve surface direction perpendicular to the plate thickness direction of the plate-like valve body. A multi-unit integrated valve opening and closing device. In the multiple integrated valve opening and closing device according to claim 25 or claim 26,
Each plate-like valve element provided for each of the plurality of valves has intake air supplied to the cylinders of the internal combustion engine by cutting away an end surface opposite to each valve shaft provided for each of the plurality of valves. A multiple-integrated type valve opening / closing device having an opening for generating a vortex flow in the valve. (A) a casing having a plurality of air flow paths that are independently connected to each cylinder of the internal combustion engine; and (b) disposed corresponding to each of the plurality of air flow paths and penetrating in the direction of the rotation axis. A plurality of valves having through holes;
(C) one shaft that is disposed so as to penetrate each through-hole formed in each valve in the direction of the rotation axis, and that couples the plurality of valves so as to be skewered;
(D) In a multiple integrated valve opening and closing device comprising an actuator that generates a driving force for driving the plurality of valves in the valve opening operation direction or the valve closing operation direction via the shaft.
The shaft has a plurality of fitting portions for holding the plurality of valves at a predetermined mounting angle;
Each valve corresponding to each of the plurality of fitting portions has a cylindrical valve shaft disposed so as to surround the periphery of the through hole, and a radial direction perpendicular to the rotation axis direction from the valve shaft. A plate-shaped valve element extended,
The casing has a plurality of cylindrical portions in which the air flow path is formed,
The plurality of cylindrical portions are used as opposing surfaces in which the flow path wall surface in the vicinity of the fully closed position of each valve faces the end surface of each plate-like valve body provided for each of the plurality of valves when the valve is fully closed. ,
Each opposed surface provided for each of the plurality of cylindrical portions is extended in the valve opening operation direction of each valve with respect to the flow path wall surface upstream of the opposed surface in the air flow direction. It is curved in an arc shape along the rotation trajectory of the valve body,
The length of the curved surface in the valve opening operation direction of each facing surface is a curve corresponding to the maximum value of the shaft twist angle generated by the load torque acting in the valve opening operation direction for each valve when the valve is fully closed. A multi-unit integrated valve opening and closing device characterized by being set to a surface length. The multiple-integrated valve opening and closing device according to claim 28,
Each valve corresponding to each of the plurality of fitting portions is a cantilever valve in which the valve shaft is biased to one side in the valve surface direction perpendicular to the plate thickness direction of the plate-like valve body. A multi-unit integrated valve opening and closing device. The multiple-integrated type valve opening and closing device according to claim 28 or claim 29,
Each plate-like valve element provided for each of the plurality of valves has intake air supplied to the cylinders of the internal combustion engine by cutting away an end surface opposite to each valve shaft provided for each of the plurality of valves. A multiple-integrated type valve opening / closing device having an opening for generating a vortex flow in the valve. The multiple-integrated valve opening / closing device according to any one of claims 11 to 30,
Each fitting portion provided on the shaft is formed in a polygonal cross-sectional shape,
Each of the through holes formed for each of the plurality of valves is formed in a polygonal hole shape corresponding to a cross-sectional shape of each of the fitting portions. The multiple-integrated valve opening and closing device according to any one of claims 1 to 31,
The multi-unit integrated valve opening / closing device, wherein the actuator has an output shaft coupled to one end of the shaft in the rotation axis direction. The multiple integrated valve opening and closing device according to claim 32,
A spring for applying a load that biases the shaft toward a side that reduces a gap formed in a coupling portion between the shaft and the output shaft of the actuator;
The multiple-integrated type valve opening and closing device, wherein the spring is disposed on the opposite side to the actuator side in the rotation axis direction of the shaft. The multiple-integrated valve opening / closing device according to any one of claims 1 to 33,
The casing is an intake manifold in which a valve unit in which the valve is incorporated in a housing in which the air flow path is formed is opened and closed in a group at regular intervals in the rotation axis direction of the shaft. A multi-unit integrated valve opening and closing device. The multiple integrated valve opening and closing device according to any one of claims 1 to 34,
The multiple-integrated type valve opening / closing device, wherein the shaft constitutes a rotation shaft that forms a rotation center of the plurality of valves. 36. The multiple integrated valve opening / closing device according to any one of claims 1 to 35,
The plurality of fitting portions are provided corresponding to the plurality of valves at regular intervals in the rotation axis direction of the shaft, and are inserted into the through holes formed for the plurality of valves. A multi-unit integrated valve opening and closing device characterized by comprising:

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