JP2008274785A - Valve unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To stabilize a leakage air flow rate during full close of an intake flow control valve 5 or an air flow rate passing through an opening 9 during the full close of the intake flow control valve 5. <P>SOLUTION: First and second valve reduced-diameter parts 31, 32 of conical surface shapes gradually reduced in diameter toward axial centers of respective first and second slide holes 21, 22 of first and second two bearings 3, 4 and first and second slide parts 33, 34 are provided on opposite ends of a rotary shaft 6 of the intake flow control valve 5, and first and second aligning guides 51, 52 of conical surface shapes are provided at open end edges on an intake passage side of the first and second two bearings 3, 4. This enables alignment between an axial center (central axis line) of the rotary shaft 6 of the intake flow control valve 5 and the axial centers (central axis lines) of the respective first and second slide holes 21, 22 of the first and second two bearings 3, 4. In other words, misalignment in axial center between the axial center of the rotary shaft 6 of the intake flow control valve 5 and the axial centers of the first and second two bearings 3, 4 is inhibited. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a valve unit in which a valve is rotatably accommodated inside a housing via a bearing member, and particularly relates to a valve unit provided in an intake system of an internal combustion engine.

[Conventional technology]
Conventionally, by generating a vertical swirling flow (tumble flow) in the combustion chamber of an internal combustion engine, the combustion efficiency in the combustion chamber is increased, fuel efficiency is improved, and engine performance such as engine output and exhaust emission is improved. An intake control device for an internal combustion engine that improves the above is known (see, for example, Patent Documents 1 and 2).
Here, the intake flow control valve (valve unit) that generates the tumble flow in the combustion chamber of the internal combustion engine, as shown in FIG. 7, is an air flow path (intake passage of the internal combustion engine) that communicates with the combustion chamber of the internal combustion engine. A housing 102 forming 101 is provided, and a valve 103 is disposed inside the housing 102 so as to be rotatable relative to the housing 102. A rotating shaft 104 is integrally formed with the valve 103.

  The housing 102 is provided with two opposing wall portions (both side wall portions) that face each other across the intake passage 101 and face both side surfaces of the valve 103. The two side wall portions are provided with two valve bearing portions 111 and 112 having bearing fitting holes (bearing holes) formed therein. Two bearings 105 and 106 are fitted and fixed in the bearing hole. Further, at the upper end of the valve 103 in the direction of gravity, a tumble flow is generated in the intake air supplied to the internal combustion engine when the valve 103 is fully closed (when the valve 103 is fully closed). An opening 107 is formed. In addition, in the two bearings 105 and 106, circular sliding holes 121 and 122 for rotatably supporting both end portions (two valve sliding portions) in the rotation axis direction of the valve 103 so as to be slidable in the rotation direction. Is formed.

[Conventional technical problems]
However, in the intake control device for an internal combustion engine including the valve unit described in Patent Documents 1 and 2, the two valve sliding portions of the rotating shaft 104 are formed in a columnar shape, and the two bearings 105 and 106 are formed in a cylindrical shape. Is formed. In addition, between the two valve sliding portions and the hole wall surfaces of the two bearings 105 and 106, in order to smoothly rotate the rotating shaft 104 of the valve 103 within the sliding holes 121 and 122, a predetermined sliding Clearance is formed.

Therefore, in the intake control device for an internal combustion engine described in Patent Documents 1 and 2, since a valve bearing structure having a predetermined sliding clearance is employed, when the valve 103 is fully closed, the amount of sliding clearance is increased. There is a possibility that the gap formed between the end surface and the housing upper wall portion of the housing 102, that is, the opening area of the opening 107 may fluctuate, and the flow rate (or valve) of the intake air passing through the opening (gap) 107 The leakage air flow rate at the time of the fully closed state 103 becomes unstable. As a result, it becomes difficult to generate an optimal tumble flow, resulting in a problem that fuel efficiency and engine performance are lowered.
JP 2007-040282 A (page 1-6, FIGS. 1 to 8) JP 2007-064176 (page 1-17, FIG. 1 to FIG. 9)

  An object of the present invention is to provide a valve unit capable of stabilizing the leakage fluid flow rate when the valve is fully closed or the fluid flow rate passing through the opening when the valve is fully closed.

  According to the first aspect of the present invention, the outer diameter of the rotating shaft of the valve is gradually reduced toward the axial center of the sliding hole so that the axial center of the sliding hole of the bearing member is the apex. In addition, an alignment guide for aligning the valve by contacting the reduced diameter portion of the rotating shaft is provided closer to the fluid flow path than the sliding hole of the bearing member. When the rotary shaft of the valve is slidably supported in the rotation direction in the sliding hole, or when the rotary shaft of the valve is assembled in the sliding hole of the bearing member, the reduced diameter portion of the rotary shaft becomes the bearing member. The valve is aligned by being guided by the alignment guide. As a result, the coaxial axis of the axis of the rotation axis of the valve and the axis of the sliding hole of the bearing member can be obtained, so that the axis of the axis of the rotation axis of the valve and the axis of the sliding hole of the bearing member can be obtained. The misalignment is suppressed.

Therefore, when the valve is fully closed (when the valve is fully closed), the gap formed between the valve and the housing is the outer peripheral surface of the rotary shaft of the valve and the hole wall surface of the bearing member. The flow rate of leakage fluid when the valve is fully closed or the flow rate of fluid passing through the opening when the valve is fully closed can be stabilized.
Here, when the valve unit is disposed in the intake system of the internal combustion engine and used as an intake vortex generator that generates an intake vortex in the combustion chamber of the internal combustion engine, the leakage air flow rate when the valve is fully closed, or the valve Since the intake air flow rate passing through the opening can be stabilized when fully closed, an optimal intake vortex flow can be generated, and fuel efficiency and engine performance can be improved.

According to the second aspect of the invention, the rotating shaft of the valve protrudes from both side surfaces in the rotating shaft direction of the valve toward both sides in the rotating shaft direction of the valve. And the rotating shaft of the valve | bulb is accommodated rotatably in the housing.
According to the third aspect of the present invention, in order to smoothly rotate the rotating shaft of the valve within the sliding hole between the sliding surface of the rotating shaft of the valve and the hole wall surface of the bearing member, a predetermined sliding is provided. Dynamic clearance is formed.
According to the fourth aspect of the present invention, the valve unit, particularly the casing for fitting and holding the housing, is provided so as to surround the periphery of the housing.

According to the fifth aspect of the present invention, the rotary shaft of the valve is provided with a large diameter portion having an outer diameter larger than the hole diameter of the sliding hole and a small diameter portion having an outer diameter smaller than the hole diameter of the sliding hole. . And the diameter-reduced part which the outer diameter reduced gradually from the large diameter part toward the small diameter part is provided in the rotating shaft of the valve | bulb.
According to the invention described in claim 6, from the wall surface of the housing toward the central axis side of the fluid flow path, the large diameter portion side of the reduced diameter portion is directly coupled to both side surfaces of the valve in the rotation axis direction. It protrudes and is exposed in the fluid flow path.
According to invention of Claim 7, the small diameter part side of the diameter reduction part is engage | inserted in the sliding hole.

According to the invention described in claim 8, the conical surface that is slidably supported by the alignment guide is provided in the reduced diameter portion of the rotating shaft. In this case, a conical surface-shaped guide surface is formed on the aligning guide of the bearing member to contact the conical surface of the reduced diameter portion and align the valve. Thereby, the rotating shaft of the valve is aligned with the guide surface of the alignment guide of the bearing member.
According to the ninth aspect of the present invention, the reduced diameter portion of the rotating shaft is provided with a convex curved surface (a convex curved surface constituting a part of a spherical surface) that is slidably supported by the alignment guide. In this case, a concave curved guide surface is formed on the alignment guide of the bearing member to contact the convex curved surface of the reduced diameter portion to align the valve. Thereby, the rotating shaft of the valve is aligned with the guide surface of the alignment guide of the bearing member.
According to the tenth aspect of the present invention, the concave surface that is slidably supported by the alignment guide is provided in the reduced diameter portion of the rotating shaft. In this case, a guide surface having a convex curved surface (a convex curved surface constituting a part of a spherical surface) is formed on the alignment guide of the bearing member to contact the concave curved surface of the reduced diameter portion and perform valve alignment. . Thereby, the rotating shaft of the valve is aligned with the guide surface of the alignment guide of the bearing member.

According to the eleventh aspect of the present invention, the fluid flow path is an intake passage of the internal combustion engine. That is, an intake passage for supplying intake air to the combustion chamber of the internal combustion engine is formed inside the housing.
According to the twelfth aspect of the present invention, the valve is provided with an opening for generating a vortex in the intake air supplied to the internal combustion engine. As a result, a longitudinal or lateral intake vortex (for example, a tumble flow or a swirl flow) can be generated in the combustion chamber of the internal combustion engine.

According to the thirteenth aspect of the present invention, by providing an opening at the upper end of the valve in the gravity direction when the valve is fully closed, a vertical intake vortex (for example, tumble) is formed in the combustion chamber of the internal combustion engine. Flow) can be generated.
According to the fourteenth aspect of the present invention, a cantilever type valve in which the rotating shaft is shifted to one end side from the central portion of the valve is employed as the valve.
According to the fifteenth aspect of the present invention, as the valve, a double-supported valve in which the rotation shaft is installed at the central portion of the valve is employed.

  In the best mode for carrying out the present invention, the purpose of stabilizing the leakage fluid flow rate when the valve is fully closed or the fluid flow rate passing through the opening when the valve is fully closed is slid onto the rotary shaft of the valve. Provided with a reduced diameter part whose outer diameter is gradually reduced toward the axial center of the sliding hole so that the axial center of the moving hole is the apex, the valve is located closer to the fluid flow path than the sliding hole of the bearing member. This was realized by providing a centering guide that contacts the reduced diameter part of the valve to align the valve.

[Configuration of Example 1]
1 to 3 show a first embodiment of the present invention. FIG. 1 shows a valve unit (cartridge). FIG. 2 shows an intake control device for an internal combustion engine. FIG. 3A is a diagram showing a fully closed position of the intake flow control valve, and FIG. 3B is a diagram showing a fully opened position of the intake flow control valve.

An intake control device for an internal combustion engine according to this embodiment includes a fluid flow path (intake passage) for supplying intake air (intake air) to a combustion chamber of each cylinder of an internal combustion engine (for example, a 4-cylinder gasoline engine: hereinafter referred to as an engine). ) And an intake vortex generator capable of generating an intake vortex for promoting combustion of the air-fuel mixture in each cylinder (cylinder) of the engine. Yes.
The intake vortex generator is incorporated in the intake system of the engine together with the throttle control device. The intake vortex generator is a multiple-integrated type in which a plurality of valve units are arranged in parallel in the axial direction (rotational axis direction) of the pin rod (shaft) 8 in the intake manifold 1 at a constant interval. This is an intake passage opening / closing device (valve opening / closing device).

  Here, the engine generates an output by heat energy obtained by combusting an air-fuel mixture of intake air and fuel in a combustion chamber, and includes an intake stroke, a compression stroke, an expansion (combustion) stroke, and an exhaust stroke. A 4-cycle engine that repeats a stroke (stroke) as a cycle is adopted. This engine is mounted in an engine room of a vehicle such as an automobile. The engine includes an intake pipe (intake duct) for introducing intake air into the combustion chamber of the engine, and an exhaust pipe for exhausting the exhaust gas flowing out from the combustion chamber of the engine to the outside via the exhaust purification device. (Exhaust duct).

  The engine has a cylinder head that is airtightly coupled to the downstream end of the intake manifold 1 and a combustion chamber in which an air-fuel mixture is sucked from an intake port (intake port) having a three-dimensional intake passage shape provided in the cylinder head. And a cylinder block that forms a cylinder. A spark plug (not shown) is attached to the cylinder head so that the tip end portion is exposed in the combustion chamber of each cylinder. The cylinder head is provided with an injector (fuel injection valve for an internal combustion engine, electromagnetic fuel injection valve: not shown) that injects fuel at an optimal timing into an intake port for each cylinder of the engine.

  The plurality of intake ports formed on one side of the cylinder head are opened and closed by poppet-type intake valves (intake valves). A plurality of exhaust ports (exhaust ports) formed on the other side of the cylinder head are opened and closed by poppet type exhaust valves (exhaust valves). A piston coupled to the crankshaft via a connecting rod is supported in a cylinder bore formed in the cylinder block of the engine so as to be slidable in the central axis direction of the cylinder bore.

  An intake pipe of an engine is a casing in which an intake passage is formed, and an air cleaner case that houses and holds an air cleaner (filtering element) that filters intake air, and a flow direction of intake air (intake air flow direction) from the air cleaner case A throttle body coupled downstream of the throttle body, a surge tank coupled downstream of the throttle body in the intake flow direction, and a double-pipe structure intake coupled downstream of the surge tank in the intake flow direction It has a manifold 1 and the like.

Here, the throttle control device of the present embodiment is a system that controls the flow rate of intake air sucked into the combustion chamber of each cylinder of the engine in accordance with the throttle opening corresponding to the valve opening of the throttle valve.
This throttle control device includes a throttle body installed in the middle of an engine intake pipe, a butterfly throttle valve that varies the amount of intake air flowing through the intake pipe (intake passage), and a direction in which the throttle valve is closed. It is configured by a return spring (or default spring) that urges (or in the valve opening operation direction).

The throttle body also includes an actuator such as an electric motor that drives a rotating shaft (rotating shaft of the throttle valve: shaft) that supports and fixes the throttle valve in the valve opening operation direction (or valve closing operation direction).
Here, the electric motor for driving the throttle valve is configured to be energized and controlled by an engine control unit (engine control device: hereinafter referred to as ECU).

Here, the intake control device (intake vortex generator) of the internal combustion engine of the present embodiment is installed in the engine room of a vehicle such as an automobile like the engine, and the combustion of the air-fuel mixture in each cylinder (cylinder) of the engine. This is a system for generating a vertical intake vortex flow (tumble flow) to promote the air flow.
This intake vortex generator is tumbled to intake manifold 1 connected downstream of the throttle body in the intake flow direction, and intake air flowing through the intake manifold 1 (first and second intake passages 11 and 12). An intake flow control valve that generates a flow (tumble flow control valve, valve unit: hereinafter referred to as TCV) and a pin rod 8 that is press-fitted to the rotary shaft 6 of the intake flow control valve 5 that is a valve body of the TCV are driven. And an ECU that controls the valve opening of the TCV in association with each system such as a throttle control device.

Inside the intake manifold 1 of the present embodiment, a first intake passage (fluid flow path) 11 having a square cross section (or rectangular cross section) and a housing storage chamber 13 having a square cross section (or rectangular cross section) are formed. ing. Each first intake passage 11 is independently connected to an intake port for each cylinder of the engine. A plurality of valve units, particularly a plurality of housings 2 are fitted and held in each housing storage chamber 13.
Further, the intake manifold 1 is formed with a shaft through hole 14 that penetrates all the housing storage chambers 13. The intake manifold 1 is installed so as to surround each housing 2, and has a plurality of polygonal cylinder portions 15 that form a first intake passage 11 and a housing storage chamber 13 therein.
Each polygonal cylinder part 15 of the intake manifold 1 constitutes a polygonal cylinder part outside the intake manifold 1 having a double-pipe structure, and has a coupling surface that is airtightly coupled to the coupling surface of the cylinder head. A rectangular (or rectangular) fitting groove into which a rectangular (or rectangular) gasket 17 is fitted is formed on the coupling surface of the intake manifold 1.

The plurality of valve units (TCV) include a housing 2 stored in the housing storage chamber 13 of the intake manifold 1 and two first support units fixed to both side walls (the left and right side walls in the drawing) of the housing 2. The second bearings 3 and 4 and the intake flow control valve 5 installed in the housing 2 (second intake passage 12) so as to be openable and closable are provided.
The housing 2 and the intake flow control valve 5 constitute a valve unit (cartridge) fitted and held in the housing storage chamber 13 of the intake manifold 1. The intake manifold 1, the plurality of housings 2, and the plurality of intake flow control valves 5 are integrally formed of a resin material.
Here, the two first and second bearings 3 and 4 have first and second cylindrical portions in which first and second sliding holes 21 and 22 are formed, respectively. The plurality of intake air flow control valves 5 have a cylindrical rotating shaft 6 that is rotatably supported inside the housing 2 via two first and second bearings 3 and 4.

The plurality of housings 2 are all made of resin and are integrally formed (resin integrated molding) with a resin material (for example, a glass fiber reinforced thermoplastic resin). These housings 2 accommodate each intake flow control valve 5 in an openable and closable manner inside, and through the two first and second bearings 3 and 4, a plurality of intake flow control valves 5 in the direction of the rotation axis. Both end portions (two first and second valve diameter-reduced portions 31, 32 and two first and second valve sliding portions 33, 34) are rotatably supported.
Here, the plurality of housings 2 are polygonal cylindrical bodies, and constitute a polygonal cylinder portion inside the intake manifold 1 having a double-pipe structure.

  These housings 2 have a pair of opposing sides on both sides in a direction orthogonal to the axial direction (intake flow direction) of each second intake passage 12 (horizontal direction perpendicular to the gravitational direction of each second intake passage 12). Each has wall portions (both side wall portions, left and right side wall portions: hereinafter, housing left and right wall portions). The plurality of housings 2 have a pair of upper and lower wall portions (top wall) on both sides in a direction (gravitational direction of each second intake passage 12) perpendicular to the axial direction (intake flow direction) of each second intake passage 12. Part, bottom wall part: the housing upper and lower wall parts).

  Here, the plurality of valve units are connected to the plurality of housings 2 corresponding to the first intake passages 11 of the intake manifold 1 and connected to the intake ports of the cylinder head. The second intake passage (fluid flow passage) 12 is provided. That is, an intake passage (fluid flow passage) 12 having a square cross section (or a rectangular cross section) is formed in each housing 2. These second intake passages 12 are arranged downstream of the first intake passages 11 of the intake manifold 1 in the intake flow direction, and are connected to the combustion chambers of the engine cylinders via a plurality of intake ports. Connected independently.

The plurality of housings 2 open at the upstream ends of the second intake passages 12 in the axial direction (intake flow direction), and intake intake ports for introducing intake air from the first intake passages 11 of the intake manifold 1. (Inlet part). The plurality of housings 2 are opened at the downstream ends in the axial direction (intake flow direction) of the respective second intake passages 12, and intake intake ports for introducing intake air from the respective second intake passages 12 to the respective intake ports. (Exit part).
Then, the left and right wall portions of each housing 2 provided for each of the plurality of housings 2 are opposed to both side surfaces (valve left and right side surfaces) of the plurality of intake flow control valves 5 in the rotation axis direction with a predetermined gap (side clearance) therebetween. A pair of side wall surfaces (opposing surfaces) are provided. Further, the left and right wall portions of each housing are disposed so that the pair of side wall surfaces face each other with the second intake passages 12 therebetween.

  In addition, two first and second bearings are provided on the lower side (bottom wall side, housing lower wall side) in the gravity direction of the second intake passage 12 of each housing left and right wall provided for each of the plurality of housings 2. 3 and 4, both ends of each intake flow control valve 5 in the rotation axis direction (two first and second valve diameter-reduced portions 31 and 32 and two first and second valve sliding portions 33 and 34. ) Are rotatably supported. Two first and second valve bearing portions 35 and 36 are provided. Two first and second bearing holes 41 and 42 are formed inside the two first and second valve bearing portions 35 and 36, respectively. Two first and second bearings (bearing members) 3 and 4 are fitted and held on the inner periphery of the first and second bearing holes 41 and 42.

  The two first and second bearings 3 and 4 are made of a metal material or a resin material in a cylindrical shape, and each of the first and second cylindrical portions is provided with two first and second bearings provided in the housing 2. It is press-fitted and fixed to the inner periphery (hole wall surface) of the holes 41 and 42. Inside each of the first and second cylindrical portions of the two first and second bearings 3 and 4 are both end portions (two first and second valve diameter reductions) in the rotation axis direction of the plurality of intake flow control valves 5. The first and second sliding holes 21 and 22 having a circular cross section for supporting the portions 31 and 32 and the two first and second valve sliding portions 33 and 34) so as to be slidable in the rotational direction are formed. Yes.

  In addition, the two first and second bearings 3 and 4 are arranged closer to the intake passage side than the first and second sliding holes 21 and 22, and the first and second shafts 6 of the plurality of intake flow control valves 5. Two first and second aligning guides 51 and 52 for aligning each intake flow control valve 5 in contact with the second valve diameter reducing portions 31 and 32 are provided. These first and second alignment guides 51 and 52 have the first and second sliding holes 21 and 22 as the apexes with the axial centers of the first and second sliding holes 21 and 22 as vertices. It has a conical surface (tapered surface) whose inner diameter is gradually reduced toward the axis.

  The plurality of intake flow control valves 5 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 5 have a rotation center axis in a direction orthogonal to the axial direction (intake flow direction) of each housing 2 and are coupled to one pin rod 8 so as to be skewered. This is a rotating type valve. In addition, the plurality of intake air flow control valves 5 are configured such that the flow rate of the intake air flowing through the second intake passages 12 is minimized from the fully open position where the flow rate of the intake air flowing through the second intake passages 12 is maximum. The rotation angle (valve opening degree) is changed in the valve operating range (valve opening / closing range) up to the fully closed position, thereby rotating relative to each housing 2 to open / close each second intake passage 12. To do.

  The plurality of intake flow control valves 5 are fully closed when the valve body is fully closed, that is, when the valve body opening degree (valve opening degree) is fully closed (closed) at the fully closed position. When in the state (when the intake flow control valve 5 is fully closed), the rotary shaft 6 is positioned on one side of the valve surface direction perpendicular to the plate thickness direction of the intake flow control valve 5 (from the valve central portion of the valve body). It is arranged at a position biased to the lower side in the figure. That is, in the valve unit (TCV) of the present embodiment, as the valve, the rotation shaft 6 that forms the rotation center of the valve body is closer to the plate thickness direction of the valve body of the intake flow control valve 5 than the valve center portion of the valve body. A cantilever type intake flow control valve that is shifted to one end side in the valve surface direction perpendicular to the vertical direction (a lower side in the gravity direction of the second intake passage 12 and a lower side in the drawing) is formed.

Here, the plurality of intake air flow control valves 5 drive the electric motor as shown in FIG. 3A when the engine is cold or when the flow rate (intake air amount) of the intake air may be small. It is fully closed using power. That is, the valve opening degree of the intake flow control valve 5 is controlled so as to be in the fully closed opening state (fully closed position).
Further, the plurality of intake air flow control valves 5 are fully opened using the driving force of the electric motor as shown in FIG. That is, the valve opening degree of the intake flow control valve 5 is controlled so as to be in the fully opened position (fully opened position).
Further, when the supply of electric power to the electric motor is stopped when the engine is stopped, the plurality of intake flow control valves 5 are in a fully opened position (or an intermediate opening state slightly closed from the fully opened position) by an urging force such as a spring, for example. (Intermediate position)).

Here, the plurality of valve units have shaft through-holes (polygonal holes) 7 penetrating in the direction of the rotation axis of the pin rod 8 for each of the plurality of intake flow control valves 5. Further, the plurality of intake flow control valves 5 include a cylindrical rotary shaft (valve shaft) 6 disposed so as to surround the shaft through-hole 7 and so as to surround the pin rod 8 in the circumferential direction, and It has a rectangular plate-shaped (or rectangular plate-shaped) valve body or the like extending from the rotation center axis of the rotation shaft 6 toward one side (one side) in the radial direction perpendicular to the rotation axis direction.
Each shaft through-hole 7 formed for each of the plurality of intake flow control valves 5 has a polygonal hole shape (square hole shape) corresponding to the cross-sectional shape (square shape) of the pin rod 8, that is, substantially the same as the cross-sectional shape of the pin rod 8. The relative rotation between the rotating shaft 6 of the intake flow control valve 5 and the pin rod 8 is restricted.

  Here, the plurality of valve units (TCV) are in the direction of gravity of each intake flow control valve 5 when all intake flow control valves 5 are fully closed (when the intake flow control valve 5 is fully closed). A rectangular opening (notch) for generating an intake vortex flow (tumble flow) in the intake air supplied to the combustion chamber of each cylinder of the engine by cutting out a part (central portion) of the valve upper end surface in Part, slit) 9 is provided. The opening 9 may not be provided. Alternatively, a sub-opening having a smaller opening area than the opening (main opening) 9 may be formed by cutting out part of the left and right side surfaces of the intake flow control valve 5.

  Here, the plurality of intake flow control valves 5 are two first and second valves protruding from both side surfaces (valve left and right side surfaces) in the rotation axis direction toward both sides in the rotation axis direction of the intake flow control valve 5. The diameter-reducing portions 31 and 32 and the two first and second valve sliding portions (small-diameter portions) 33 and 34 are provided. The two first and second valve diameter-reduced portions 31 and 32 and the two first and second valve sliding portions 33 and 34 correspond to both ends of the plurality of intake flow control valves 5 in the rotation axis direction. . Further, the plurality of intake flow control valves 5 have outer diameters larger than the diameters of the first and second sliding holes 21 and 22 for each of the plurality of rotation shafts 6 provided integrally with each other. The first and second large diameter portions 25 and 26 are provided.

The two first and second valve diameter-reduced portions 31 and 32 have the first and second sliding holes 21 and 22 so that the axial centers of the first and second sliding holes 21 and 22 are the apexes. It has a conical surface (tapered surface) whose outer diameter is gradually reduced toward the axial center. The conical surface gradually decreases in outer diameter from the first and second large diameter portions 25 and 26 on the intake passage side (valve body side) toward the first and second valve sliding portions 33 and 34. Furthermore, the first and second alignment guides 51 and 52 of the two first and second bearings 3 and 4 are in contact with each other on the same circumference so as to be slidable in the rotational direction. It is pivotally supported.
The large diameter portions of the two first and second valve diameter-reduced portions 31 and 32 are connected to the left and right side surfaces of each intake flow control valve 5 directly from the passage wall surface of the housing 2 to the second intake passage 12. It protrudes toward the central axis side and is exposed in the second intake passage 12. In addition, the valve sliding part (small diameter part) side of the two first and second valve diameter-reduced parts 31 and 32 is the first and second sliding holes 21 of the two first and second bearings 3 and 4, respectively. , 22.

Further, the two first and second valve sliding portions 33 and 34 are small-diameter portions having an outer diameter smaller than the hole diameters of the first and second sliding holes 21 and 22, and the rotation of each rotary shaft 6. It is provided at both ends in the axial direction. The outer diameter surfaces of the first and second valve sliding portions 33 and 34 are between the hole wall surfaces of the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4. Function as two first and second valve sliding surfaces that form a predetermined sliding clearance.
Further, the tip ends of the two first and second valve sliding portions 33 and 34 in the rotation axis direction are the first and second opening end surfaces (annular end surfaces) of the two first and second bearings 3 and 4. It protrudes toward both sides in the rotational axis direction. The two first and second valve sliding portions 33 and 34 may not protrude from the first and second opening end surfaces (annular end surfaces) of the two first and second bearings 3 and 4. . That is, even if the two first and second valve sliding portions 33 and 34 are entirely fitted in the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4, respectively. good.
The two first and second valve diameter-reduced portions 31 and 32 and the two first and second valve sliding portions 33 and 34 are respectively connected to the first and second bearing holes of the plurality of housings 2. 41 and 42 are rotatably accommodated.

Here, the pin rod 8 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) by, for example, an iron-based metal material. The pin rod 8 is inserted into each shaft through hole 7 formed for each of the plurality of intake flow control valves 5. The pin rod 8 is a single drive shaft that connects all the intake flow control valves 5 so as to be interlocked by connecting the rotary shafts 6 of the plurality of intake flow control valves 5 so as to be in a skewed state. The pin rod 8 is press-fitted and fixed to the hole wall surface of the shaft through hole 7 of each rotating shaft 6 provided for each of the plurality of intake flow control valves 5.
Even if the pin rod 8 having a polygonal cross section is directly supported by the first and second bearing holes 41 and 42 of the two first and second valve bearing portions 35 and 36 of the housing 2, the pin rod 8 can be smoothly moved. Cannot be rotated. For this reason, the pin rod 8 of the present embodiment is covered with each rotating shaft 6, and the outer peripheral side is rotatably supported on the inner peripheral surfaces of the two first and second bearings 3 and 4 via the rotating shaft 6. Yes.

Here, the electric motor that drives the intake flow control valve 5 via the pin rod 8 is configured to be energized and controlled by the ECU. The ECU includes a CPU for performing control processing and arithmetic processing, a storage device (memory such as ROM and RAM) for storing a control program or control logic and various data, an input circuit (input unit), an output circuit (output unit), A microcomputer having a known structure configured to include functions such as a power supply circuit and a timer is provided.
Further, when the ignition switch is turned on (IG / ON), the ECU controls energization of the electric motor of the intake vortex generator and the electric motor of the throttle controller based on the control program or control logic stored in the memory. In addition, an ignition device (ignition coil, spark plug, etc.) and a fuel injection device (electric fuel pump, injector, etc.) are driven. Thus, during the operation of the engine, the valve opening of the TCV, the intake air amount, the fuel injection amount, and the like are controlled so as to become control command values (control target values), respectively.
Further, when the ignition switch is turned off (IG / OFF), the ECU forcibly terminates engine control including ignition control and fuel injection control based on a control program or control logic stored in the memory. It is configured as follows.

[Operation of Example 1]
Next, the operation of the intake control device (intake vortex generator) for the internal combustion engine of this embodiment will be briefly described with reference to FIGS.

  When the ignition switch is turned on (IG / ON), the ECU controls energization of the electric motor of the throttle control device, as well as an ignition device (ignition coil, spark plug, etc.) and a fuel injection device (electric fuel pump, injector, etc.) Drive. As a result, the engine is operated. At this time, when the specific cylinder of the engine moves from the exhaust stroke to the intake stroke where the intake valve opens and the piston descends, the negative pressure (pressure lower than the atmospheric pressure) in the combustion chamber of the cylinder is reduced as the piston descends. The air-fuel mixture is sucked into the combustion chamber from the intake port that is enlarged and opened.

Further, the ECU controls the power supplied to the electric motor (for example, energizes the electric motor) when the engine is warm and the intake air flow rate (intake amount) is large, that is, during normal operation of the engine. At this time, since the intake flow control valve 5 is driven in the valve opening operation direction using the driving force of the electric motor, it is opened. That is, the valve opening of the TCV is controlled so as to be in a state where the valve is opened at the fully opened position (a state of the fully opened opening).
In this case, the intake air flow that flows from the plurality of first intake passages 11 of the intake manifold 1 of the engine into the respective second intake passages 12 formed for each of the plurality of housings 2 through the inlet portions of the respective housings 2 of the TCV is It passes straight through the plurality of second intake passages 12 and is introduced into the intake ports provided in the cylinder heads of the engine from the outlets of the plurality of housings 2. The intake air flow that has passed through the intake port is supplied from the intake valve port of the intake port 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 flow rate (intake amount) of the intake air may be small, that is, when the engine is started or idling. To do. At this time, the intake flow control valve 5 is closed because it is driven in the valve closing operation direction using the driving force of the electric motor. That is, the valve opening of the TCV is controlled so as to be in a closed state at the fully closed position (a state of the fully closed opening).
In this case, the intake air flow that flows into the plurality of second intake passages 12 from the plurality of first intake passages 11 of the intake manifold 1 of the engine via the inlet portions of the plurality of housings 2 is almost above the valve of the intake flow control valve 5. Passing only through the gap (opening 9) between the end surface and the housing upper wall portion of the housing 2, it is introduced into the upper layer portion of each intake port from the outlet portion of the plurality of housings 2, and the top of the upper layer portion of the intake port Flows along the wall. And the intake flow which flows along the top wall of the upper layer part of the intake port is supplied into the combustion chamber from the intake valve port of the intake port. 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

[Effect of Example 1]
As described above, in the intake air control device (intake vortex generator) for the internal combustion engine of the present embodiment, the intake flow control valve 5 in which the opening 9 is formed on the upper end surface of the valve is positioned below the center of the valve. Cylindrical rotating shaft 6 that is rotatably supported by two first and second valve bearing portions 35 and 36 installed in housing 2 is provided via two first and second bearings 3 and 4. ing. Then, each of the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4 is arranged on the rotary shaft 6 of the intake flow control valve 5 so that the axis centers thereof are the apexes. First and second valve diameter-reduced portions 31 and 32 having tapered conical surfaces whose outer diameters are gradually reduced toward the axial centers of the first and second sliding holes 21 and 22 are provided.

  The two first and second bearings 3 and 4 are connected to the intake passage side of the first and second sliding holes 21 and 22, respectively, and the first and second valve diameters of the intake flow control valve 5 are reduced. By providing the two first and second alignment guides 51 and 52 that contact the portions 31 and 32 to align the intake flow control valve 5, each of the two first and second bearings 3 and 4 is provided. When the rotary shaft 6 of the intake flow control valve 5 is slidably supported in the rotational direction in the first and second sliding holes 21 and 22, or each of the first and second bearings 3 and 4 is supported. When the rotary shaft 6 of the intake flow control valve 5 is assembled in the first and second sliding holes 21 and 22, the tapered conical surfaces of the first and second valve diameter-reduced portions 31 and 32 of the rotary shaft 6 Are guided by the conical surfaces (tapered surfaces) of the two first and second alignment guides 51 and 52 of the two first and second bearings 3 and 4, respectively. Flow control valve 5 is the alignment.

Thus, the first and second valve sliding surfaces of the two first and second valve sliding portions 33 and 34 of the rotating shaft 6 of the intake flow control valve 5 and the two first and second bearings 3 and 4 are provided. Even if a predetermined sliding clearance is formed between the wall surfaces of the first and second sliding holes 21 and 22, the axis of the rotary shaft 6 of the intake flow control valve 5 and the two first The second bearings 3 and 4 can be coaxial with the axis of the first and second sliding holes 21 and 22.
That is, the axis of the rotary shaft 6 of the intake flow control valve 5 and the axes of the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4 are arranged on the same axis. In this state, the intake flow control valve 5 is rotatably accommodated inside the housing 2, so that the axis of the rotation shaft 6 of the intake flow control valve 5 and the first and second bearings 3, 4 are respectively 1, the coaxiality with the axial center of the second sliding holes 21 and 22 is improved, the axial center of the rotating shaft 6 of the intake flow control valve 5 and the first and second bearings 3 and 4 of each of the first and second bearings 3 and 4, respectively. Axial misalignment with the axial center of the second sliding holes 21 and 22 is suppressed.

Therefore, when the intake flow control valve 5 is fully closed, a gap formed between the upper end surface of the intake flow control valve 5 and the top wall surface of the upper wall of the housing 2, that is, the opening 9 is the intake flow control. The first and second valve sliding surfaces of the two first and second valve sliding portions 33 and 34 of the rotary shaft 6 of the valve 5 and the first and second of the first and second bearings 3 and 4, respectively. 2 The amount of leakage air when the intake flow control valve 5 is fully closed or the entire flow of the intake flow control valve 5 does not vary by the sliding clearance formed between the wall surfaces of the two slide holes 21 and 22. The flow rate of the intake air that passes through the opening 9 when closed can be stabilized.
Therefore, in the intake control device (intake vortex generator) for the internal combustion engine of the present embodiment, an optimal intake vortex (tumble flow) can be generated, and fuel efficiency and engine performance can be improved.

  Further, the valve unit (TCV) of this embodiment includes two first and second bearings 3, 4 that are press-fitted and fixed to the hole wall surfaces of the two first and second bearing holes 41, 42 provided in the housing 2. On the conical surfaces (tapered surfaces) of the first and second alignment guides 51 and 52 and the outer diameter surfaces of the first and second valve diameter-reduced portions 31 and 32 of the rotary shaft 6 of the intake flow control valve 5. The taper-shaped conical surface provided is opposed to be always in sliding contact. The first and second alignment guides 51 and 52 of the two first and second bearings 3 and 4 have the same cross-sectional shape, and the first and second valve diameter-reduced portions 31 of the rotary shaft 6 are the same. , 32 have the same cross-sectional shape.

Accordingly, since the position of the intake flow control valve 5 in the rotation axis direction with respect to the housing 2 is defined to be a predetermined position, the left and right side surfaces of the plurality of intake flow control valves 5 and the both sides of the housing left and right wall portions of the housing 2 are defined. The side clearances on both sides in the rotation axis direction for each of the plurality of intake flow control valves 5 can be equalized without sandwiching shims between the wall surfaces (opposing surfaces).
As a result, the plurality of intake flow control valves 5 for each housing storage chamber 13 (and each second intake passage 12 formed for each of the plurality of housings 2) formed for each of the plurality of polygonal cylinder portions 15 of the intake manifold 1. Eccentric assembly can be prevented.

  FIG. 4 shows a second embodiment of the present invention and shows a valve unit (cartridge).

  The two first and second bearings 3 and 4 of this embodiment have two first and second alignment guides 51 and 52 on the intake passage side of the first and second sliding holes 21 and 22, respectively. is doing. These first and second alignment guides 51 and 52 rotatably support both end portions (two first and second reduced-diameter portions 31 and 32) of the rotary shaft 6 of the intake flow control valve 5. It has a concave curved surface. Further, the two first and second valve diameter-reduced portions 31 and 32 of the rotary shaft 6 of the intake flow control valve 5 slide in the rotational direction on the concave curved surfaces of the two first and second centering guides 51 and 52. It has a spherical convex curved surface that is freely supported.

In the valve unit of this embodiment, the rotary shaft 6 of the intake flow control valve 5 is slidable in the rotation direction in the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4. When the rotary shaft 6 of the intake flow control valve 5 is assembled to the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4, respectively. 6 are guided by the concave curved surfaces of the two first and second aligning guides 51 and 52 of the two first and second bearings 3 and 4, respectively. Thus, the intake flow control valve 5 is aligned.
As a result, the same effects as those of the first embodiment can be obtained.

  FIG. 5 shows a third embodiment of the present invention and is a view showing a valve unit (cartridge).

  The two first and second bearings 3 and 4 of this embodiment have two first and second alignment guides 51 and 52 on the intake passage side of the first and second sliding holes 21 and 22, respectively. is doing. These first and second alignment guides 51 and 52 rotatably support both end portions (two first and second reduced-diameter portions 31 and 32) of the rotary shaft 6 of the intake flow control valve 5. It has a mortar-shaped convex curved surface. Further, the two first and second valve diameter-reduced portions 31 and 32 of the rotary shaft 6 of the intake flow control valve 5 slide in the rotational direction on the convex curved surfaces of the two first and second centering guides 51 and 52. It has a truncated cone-shaped concave curved surface that is freely supported.

In the valve unit of this embodiment, the rotary shaft 6 of the intake flow control valve 5 is slidable in the rotation direction in the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4. When the rotary shaft 6 of the intake flow control valve 5 is assembled to the first and second sliding holes 21 and 22 of the two first and second bearings 3 and 4, respectively. 6 are guided by the convex curved surfaces of the two first and second alignment guides 51 and 52 of the two first and second bearings 3 and 4, respectively. Thus, the intake flow control valve 5 is aligned.
As a result, the same effects as those of the first embodiment can be obtained.

  FIG. 6 shows a fourth embodiment of the present invention. FIG. 6 (a) is a sectional view showing the fully closed position of the intake flow control valve, and FIG. 6 (b) shows the fully opened position of the intake flow control valve. FIG.

  The valve unit (TCV) of this embodiment is a double-ended valve in which the rotary shaft 6 is installed as a valve substantially at the center of the valve in the valve surface direction perpendicular to the plate thickness direction of the valve body of the intake flow control valve 5. The intake air flow control valve (butterfly type valve) is used. Further, the valve unit (TCV) is formed by cutting out the valve upper end surface on one end side (the upper end side in the drawing) in the valve surface direction perpendicular to the plate thickness direction of the valve body of the intake flow control valve 5. A rectangular opening 9 for generating an intake vortex flow (tumble flow) in the intake air supplied into the combustion chamber for each cylinder is formed.

[Modification]
In this embodiment, the intake vortex generator is configured to generate a vertical intake vortex (tumble flow) for promoting the combustion of the air-fuel mixture in the combustion chamber of the internal combustion engine. The generator may be configured to be able to generate a lateral intake vortex (swirl) for promoting the combustion of the air-fuel mixture in the combustion chamber of the internal combustion 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 valve unit of the present invention is incorporated in an intake control device for an internal combustion engine that controls intake air sucked into the combustion chamber of the internal combustion engine. However, the valve unit of the present invention is incorporated in the combustion chamber of the internal combustion engine. It may also be incorporated in an intake control device (throttle control device) for an internal combustion engine that controls the flow rate of the intake air sucked into the engine. In this case, an intake flow rate control valve such as an idle rotation speed control valve or a throttle valve is incorporated in the housing (throttle body or the like).

  Further, the valve unit of the present invention includes a housing that forms an exhaust gas recirculation path (fluid flow path) that recirculates a part of exhaust gas (EGR gas) of the internal combustion engine from the exhaust path to the intake path, and the housing. You may apply to the exhaust-gas recirculation apparatus (EGR control valve unit) accommodated so that opening and closing is possible, and provided with the EGR control valve which controls an exhaust gas recirculation amount. Further, the valve unit of the present invention includes a housing having an air flow path communicating with the exhaust passage of the internal combustion engine, and an exhaust that is housed in the housing so as to be openable and closable, and controls exhaust gas flowing out from the combustion chamber of the internal combustion engine. You may apply to the exhaust control valve unit provided with the control valve.

In addition, the valve unit of the present invention includes a variable intake valve for an internal combustion engine including a housing such as an intake manifold and a variable intake valve that changes a passage length and a passage sectional area of the intake passage of the intake manifold in accordance with the engine rotation speed. It may be incorporated into the device.
In addition to the housing 2 housed in the intake manifold 1, the intake manifold itself, the cylinder head of the internal combustion engine, and an intake pipe excluding the intake manifold may be used as the housing.
Further, as the fluid, not only a gas such as intake air or exhaust gas but also a liquid such as water, oil, or fuel may be used.

  In this embodiment, the valve drive device (actuator) for driving the rotary shaft 6 of the intake flow control valve 5 to open or close is constituted by an electric actuator provided with an electric motor and a power transmission mechanism. Actuator that opens or closes the shaft is driven by a negative pressure actuator with an electromagnetic or electric negative pressure control valve, or an electromagnetic actuator with an electromagnet such as a coil and a moving core (or armature). It may be configured.

In this embodiment, the valve unit of the present invention is mounted on an intake system (or exhaust system) of an in-line four-cylinder internal combustion engine in which cylinders are arranged in groups. However, the valve units of the invention are arranged in groups. It may be mounted on an intake system (or exhaust system) of an internal combustion engine having a plurality of banks. Such internal combustion engines include multi-cylinder engines such as V-type engines, horizontal engines, and horizontally opposed engines.
Further, although the two first and second bearings 3 and 4 are made of metal, at least one of the two first and second bearings 3 and 4 may be made of resin.
In addition, the valve is not limited to a multiple integral type valve, and if it is a valve installed in a fluid flow path, particularly a valve shaft integral type valve, one cantilever valve or one double-end valve is provided. Any of the valves of the formula may be used.

(Example 1) which is sectional drawing which showed the valve unit (cartridge). 1 is a perspective view showing an intake control device for an internal combustion engine (Example 1). FIG. (A) is sectional drawing which showed the fully closed position of the intake flow control valve, (b) is sectional drawing which showed the fully open position of the intake flow control valve (Example 1). (Example 2) which is sectional drawing which showed the valve unit (cartridge). (Example 3) which is sectional drawing which showed the valve unit (cartridge). (A) is sectional drawing which showed the fully closed position of the intake flow control valve, (b) is sectional drawing which showed the fully open position of the intake flow control valve (Example 4). It is sectional drawing which showed the intake control device of the internal combustion engine (prior art).

Explanation of symbols

1 Intake manifold 2 Housing 3 First bearing (bearing member)
4 Second bearing (bearing member)
5 Intake flow control valve 6 Rotating shaft of intake flow control valve 7 Shaft through hole (square hole) of rotating shaft
8 Pin rod (shaft)
9 Opening of intake flow control valve 11 First intake passage (fluid flow passage) of intake manifold
12 Second intake passage (fluid flow path) of housing
21 1st sliding hole of 1st bearing 22 2nd sliding hole of 2nd bearing 25 1st large diameter part of a rotating shaft 26 2nd large diameter part of a rotating shaft 31 1st valve | bulb reduced diameter part of a rotating shaft 32 rotation Second valve diameter-reduced portion of shaft 33 First valve sliding portion (small-diameter portion) of rotating shaft
34 Second valve sliding part (small diameter part) of rotating shaft
35 First valve bearing portion of housing 36 Second valve bearing portion of housing 41 First bearing hole of housing 42 Second bearing hole of housing 51 First alignment guide of first bearing 52 Second alignment guide of second bearing

Claims (15)

(A) a housing having a fluid flow path formed therein;
(B) a bearing member supported by the housing and having a sliding hole formed therein;
(C) a valve unit having a rotating shaft rotatably supported by the housing via the bearing member and including a valve for opening and closing the fluid flow path;
The rotating shaft has a reduced diameter portion whose outer diameter is gradually reduced toward the axial center of the sliding hole so that the axial center of the sliding hole is a vertex.
The valve unit, wherein the bearing member has an alignment guide for aligning the valve in contact with the reduced diameter portion on the fluid flow path side of the sliding hole. The valve unit according to claim 1, wherein
The valve unit is characterized in that the rotary shaft protrudes from both side surfaces in the rotary shaft direction of the valve toward both sides in the rotary shaft direction of the valve and is rotatably accommodated in the housing. The valve unit according to claim 1 or 2,
The valve unit according to claim 1, wherein the rotary shaft has a sliding surface that forms a predetermined sliding clearance with a hole wall surface of the bearing member. In the valve unit according to any one of claims 1 to 3,
A valve unit comprising a casing that is installed so as to surround the housing and that fits and holds the housing. In the valve unit according to any one of claims 1 to 4,
The rotating shaft has a large-diameter portion having an outer diameter larger than the hole diameter of the sliding hole, and a small-diameter portion having an outer diameter smaller than the hole diameter of the sliding hole,
The reduced diameter portion is provided such that an outer diameter gradually decreases from the large diameter portion toward the small diameter portion. The valve unit according to claim 5,
The large diameter portion side of the reduced diameter portion protrudes from the passage wall surface of the housing toward the central axis side of the fluid flow channel so as to be directly coupled to both side surfaces of the valve in the rotation axis direction. A valve unit that is exposed inside. The valve unit according to claim 5 or 6,
The small diameter part side of the said diameter reduction part is engage | inserted in the said sliding hole, The valve unit characterized by the above-mentioned. The valve unit according to any one of claims 1 to 7,
The reduced diameter portion has a conical surface that is slidably supported by the alignment guide. The valve unit according to any one of claims 1 to 7,
The reduced diameter portion has a convex curved surface that is slidably supported by the alignment guide. The valve unit according to any one of claims 1 to 7,
The reduced diameter portion has a concave curved surface that is slidably supported by the alignment guide. The valve unit according to any one of claims 1 to 10,
The valve unit characterized in that the fluid flow path is an intake passage of an internal combustion engine. The valve unit according to claim 11, wherein
The valve unit has an opening for generating a vortex in the intake air supplied to the internal combustion engine. The valve unit according to claim 12,
The valve unit is characterized in that the opening is provided at an upper end in the gravity direction of the valve when the valve is fully closed. The valve unit according to any one of claims 1 to 13,
The valve unit according to claim 1, wherein the valve is a cantilever valve in which the rotation shaft is shifted to one end side from a central part of the valve. The valve unit according to any one of claims 1 to 13,
The valve unit according to claim 1, wherein the valve is a double-supported valve in which the rotation shaft is installed at a central part of the valve.

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