JP2007162902A - Actuator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve valve retaining force at a valve full-close position of an intake air swirling current control valve, and to prevent deterioration of operation efficiency of a gear reduction mechanism in operating the intake air swirling current control valve. <P>SOLUTION: When rotating motion of the intake air swirling current control valve is regulated at the valve full-close position, two first and second rotators 31, 32 constituting an output gear 23 are relatively displaced to axial both sides, thus the total height of a structure of the output gear 23 is increased. Further as the first rotator 31 is pressed to a first regulation face 36 by axial spring load generated on a cylindrical coil portion 90 of a torsion coil spring 9, sliding resistance of the first rotator 31 of the output gear 23 is increased. Accordingly, rotating motion of the output gear 23 is regulated (locked), and the rotating motion of the intake air swirling current control valve can be locked at the valve full-close position. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an actuator having a power transmission mechanism that transmits a driving force of a power source to a moving body, and in particular, only when the moving body (valve) is stopped, of the two first and second rotating bodies. Friction force applying means for applying a friction force to the first rotating body disposed on the power source side relative to the second rotating body disposed on the valve side is disposed on the power transmission path of the power transmission mechanism. Related to the actuator.

[Conventional technology]
Conventionally, for example, a power transmission device having a reverse rotation preventing function capable of maintaining a stopped state of a valve that opens and closes a fluid flow path has been proposed (see, for example, Patent Document 1). This includes a gear reduction mechanism including a motor shaft of an electric motor and an output shaft that drives a valve, and the driving force of the electric motor (rotational torque that rotates the valve and the output shaft in the normal rotation direction) is transmitted via the gear reduction mechanism. The valve is operated to close to the output shaft, and when the valve or a component linked to the output shaft collides with the valve stopper that regulates the fully closed position, reverse rotation torque is applied to rotate the output shaft in the reverse direction from the valve side. The reverse rotation prevention function prevents the output shaft from rotating in the reverse rotation direction.

  As a gear reduction mechanism, a pinion gear fixed to the motor shaft of the electric motor, a first gear disposed so as to surround the periphery of the intermediate shaft, and meshed with the pinion gear to transmit motor torque, and an outer periphery of the output shaft And a second gear that is engaged with the first gear to transmit the motor torque. The power transmission device is provided with friction force applying means that can always apply a resistance caused by friction to the first gear on the power transmission path of the gear reduction mechanism during operation of the electric motor. Thereby, when the power transmission device is in a stationary (holding) state, the holding performance of the valve is improved by the static frictional force of the sliding resistance.

[Conventional technical problems]
However, in the power transmission device described in Patent Document 1, self-locking is improved by applying frictional resistance to the first gear on the power transmission path of the gear reduction mechanism. The reduction in the operation efficiency due to the dynamic friction force during the valve closing operation is not zero. That is, as shown in the graph of FIG. 8A, the operation efficiency due to the dynamic friction force when the valve is closed, for example, is lower than when the frictional force applying means is not set. Further, for example, the operation efficiency due to the static frictional force when the valve is regulated at the fully closed position and the valve is in a stationary (holding) state is also lowered.

  Here, it is generally arranged in the intake passage of the intake system of the internal combustion engine or the exhaust passage of the exhaust system, or in the exhaust gas recirculation path for recirculating a part of the exhaust gas flowing out from the internal combustion engine to the intake system of the internal combustion engine. When the valve body (valve) of the two-position flow control valve is controlled by a motor actuator equipped with an electric motor and a power transmission mechanism, the retention of the valve in a stopped state (self-locking) is a problem. In many cases, the valve position is one of two valve positions. For example, in the case of two positions, a fully closed position where the flow rate flowing through the fluid flow path is minimum and a fully open position where the flow rate flowing through the fluid flow path is maximum, it is necessary to maintain the airtightness of the fluid flow path. For this reason, the retaining property (self-locking property) in the fully closed position becomes a problem.

That is, in a motor actuator that variably controls the valve position, at a position that requires a large valve holding force (fully closed position), for example, in a valve closing operation direction or a valve opening operation direction while exhibiting the necessary holding force. Development of a motor actuator with good operating efficiency is demanded.
JP 2004-301278 (page 1-8, FIGS. 1-2)

  An object of the present invention is to provide a frictional force applying means that applies a frictional force to at least one of the two first and second rotating bodies only when the moving body is stopped. It is an object of the present invention to provide an actuator that can improve the moving body holding force of the moving body holding mechanism at the operation stop position and can prevent a reduction in the operating efficiency of the power transmission mechanism during operation of the moving body.

  According to the first aspect of the present invention, the first and second rotating bodies are arranged in the power transmission mechanism so as to surround the shaft. The first rotating body of the two first and second rotating bodies is arranged on the power source side of the second rotating body on the power transmission path of the power transmission mechanism. The second rotating body among the first and second rotating bodies is disposed closer to the moving body than the first rotating body on the power transmission path of the power transmission mechanism. The two first and second rotating bodies are configured to rotate integrally within an operating range of the moving body from the operation start position of the moving body to the operation stop position of the moving body.

  The moving body holding mechanism that holds the moving body at the operation stop position of the moving body is provided with frictional force applying means on the power transmission path of the power transmission mechanism. The first and second rotating bodies are coupled so as to be able to transmit power. The frictional force applying means is configured such that when the movement of the moving body is stopped (when the movement of the moving body is stopped), the further movement of the moving body is restricted (locked) at the operation stop position of the moving body. ) Only, the frictional force is applied to at least one of the two first and second rotating bodies, thereby improving the moving body holding force of the moving body holding mechanism at the operation stop position of the moving body. In addition, it is possible to prevent a reduction in operating efficiency of the power transmission mechanism when the moving body is operating.

  According to the invention described in claim 2 and claim 3, within the operating range of the moving body from the operation start position of the moving body to the operation stop position of the moving body, the two first and second rotating bodies are Although it rotates as a unit, the movement of the moving body is restricted (locked) at the operation stop position of the moving body, and when the operation of the moving body stops, it moves on the power transmission path of the power transmission mechanism. The rotation operation of the second rotating body disposed on the body side is also restricted (locked). Accordingly, when the first rotating body disposed on the power source side on the power transmission path of the power transmission mechanism is further driven and rotated by the power source, the first rotating body rotates relative to the second rotating body. . At the same time, the helical first screw provided on the first rotating body and the helical second screw provided on the second rotating body are screw-coupled, so that the two first and second rotating bodies are They are displaced relative to each other in the axial direction.

  According to the fourth aspect of the present invention, the movable body holding mechanism is provided with the restricting portion. This restricting part is a component that restricts the maximum displacement amount of at least one of the two first and second rotating bodies when the two first and second rotating bodies are displaced relative to each other. And the load application means is provided in the frictional force application means. The load applying means is provided only when at least one of the two first and second rotating bodies is used with respect to at least one of the two first and second rotating bodies. This is a component that applies a load in a direction in which the rotating body is pressed against the restricting portion. Here, the frictional force applying means including the load applying means is disposed on the power transmission path of the power transmission mechanism and can transmit power to the two first and second rotating bodies. It is combined to become.

  Thus, as described in claim 3, when the operation of the moving body is stopped, the rotation operation of the second rotating body is restricted (locked), and when the first rotating body rotates relative to the second rotating body, The application means is twisted up. As a result, a load is applied in a direction in which at least one of the two first and second rotating bodies is pressed against the regulating portion with respect to at least one of the two first and second rotating bodies. Occurs. Or the load of the direction which presses at least one rotary body out of two 1st, 2nd rotary bodies against a control part becomes large. Thereby, only when the operation of the moving body is stopped, at least one of the two first and second rotating bodies is pressed against the restricting portion of the moving body holding mechanism, whereby the two first and second rotating bodies are pressed. Since the frictional force is applied to at least one of the rotating bodies, the moving body is locked at the operation stop position. Therefore, the moving body holding force of the moving body holding mechanism at the operation stop position of the moving body can be improved, and a decrease in the operating efficiency of the power transmission mechanism during the operation of the moving body can be prevented.

  According to the fifth aspect of the present invention, the rotating body storage chamber for storing at least two of the first and second rotating bodies relative to the housing is provided inside the housing of the movable body holding mechanism. Forming. According to the sixth aspect of the present invention, the movable body is within the operating range between the regulating surface of the housing and the contact surface of at least one of the two first and second rotating bodies. , A predetermined clearance required for at least one of the two first and second rotating bodies to rotate is formed in the rotating body accommodation chamber.

  As a result, the rotational operation of the second rotating body is restricted (locked) when the operation of the moving body is stopped, and the first rotating body rotates relative to the second rotating body. Are relatively displaced from each other, the clearance between the contact surface of at least one of the two first and second rotating bodies and the regulating surface of the housing becomes 0 (zero), and the load of the load applying means Accordingly, the contact surface of at least one of the two first and second rotating bodies is pressed against the regulating surface of the housing, and at least one of the two first and second rotating bodies rotates. Since the frictional force is applied to the body, the moving body is locked at the operation stop position. Therefore, the moving body holding force of the moving body holding mechanism at the operation stop position of the moving body can be improved, and a decrease in the operating efficiency of the power transmission mechanism during the operation of the moving body can be prevented.

  According to the seventh aspect of the present invention, a spring that is twisted in the rotation direction of the first rotating body when the first rotating body rotates relative to the second rotating body is used as the load applying means. Also good. According to the invention described in claim 8, as the load applying means, rubber that is twisted in the rotation direction of the first rotating body when the first rotating body rotates relative to the second rotating body is adopted. You may do it. Furthermore, according to the ninth aspect of the present invention, the final gear or the intermediate gear disposed on the power transmission path of the power transmission mechanism may be constituted by the two first and second rotating bodies. According to the invention described in claim 10, the valve of the air flow rate control valve that controls the amount of air flowing from the intake passage into the combustion chamber of the internal combustion engine by changing the opening area of the intake passage. It may be used as a body. The air flow rate control valve may be used as a throttle valve or an idle rotation speed control valve.

  According to the eleventh aspect of the present invention, there is provided an intake vortex control valve for generating a vortex in the air flowing from the intake passage into the combustion chamber of the internal combustion engine by switching the opening area of the intake passage in two stages. It may be used as a valve body. The intake vortex flow control valve may be used as a swirl flow control valve that generates a lateral vortex flow in the air flowing into the combustion chamber from the intake passage. In addition, the intake vortex flow control valve may be used as a tumble flow control valve that generates a vertical vortex flow in the air flowing into the combustion chamber from the intake passage. Furthermore, the moving body may be a rotating body that has a drive shaft that is drivingly connected to the power transmission mechanism and that performs a rotational motion integrally with the drive shaft. In addition, a movement direction conversion mechanism that converts the rotational movement of the speed reduction mechanism into a linear movement is interposed between the power transmission mechanism and the moving body, and the moving body has a drive shaft that is drivingly connected to the movement direction conversion mechanism. However, it may be a moving body such as a valve that linearly moves integrally with the drive shaft.

  The best mode for carrying out the present invention improves the moving body holding force of the moving body holding mechanism at the operation stop position of the moving body, and prevents a reduction in operating efficiency of the power transmission mechanism when the moving body operates. This object is realized by providing a friction force applying means for applying a friction force to at least one of the two first and second rotating bodies only when the operation of the moving body is stopped.

[Configuration of Example 1]
1 to 6 show a first embodiment of the present invention, FIG. 1 is a diagram showing a schematic configuration of an intake vortex generator for an internal combustion engine, and FIG. 2 is a diagram showing an overall structure of a motor actuator. is there.

  An intake system for an internal combustion engine (intake device for an internal combustion engine) of this embodiment is provided in an intake system of an internal combustion engine (hereinafter referred to as an engine) mounted on a vehicle such as an automobile. This intake system for an internal combustion engine includes an intake vortex generator for an internal combustion engine capable of generating a lateral intake vortex (swirl) for accelerating combustion of fuel or air-fuel mixture in a combustion chamber of a cylinder of the engine. I have.

  The intake vortex generator for an internal combustion engine includes a cylindrical housing 1 provided integrally with an engine cylinder head, and intake air accommodated in the housing 1 (for example, inside an engine intake port) so as to be freely opened and closed. A vortex control valve and a coil spring (valve urging means: not shown) for urging a valve body (hereinafter referred to as an intake vortex control valve) 2 of the intake vortex control valve in a fully open direction (or a fully closed direction) I have. Further, a motor actuator (valve driving device) 3 that drives the intake vortex control valve 2 to close (or opens) the valve includes an electric motor 4 as a power source and a motor of the electric motor 4 as shown in FIG. A power transmission mechanism having an output shaft (valve shaft and drive shaft of the intake vortex control valve 2) 13 for transmitting the rotational motion of the shaft (output shaft) 11 to the intake vortex control valve 2, and the intake vortex control valve 2 are fully closed. It is configured by a valve holding mechanism (moving body holding mechanism) or the like that holds (locks) in position. The intake system for an internal combustion engine includes an engine control unit (hereinafter referred to as ECU: not shown) that electronically controls the electric motor 4 based on the operating state of the engine.

  The interior of the housing 1, that is, the intake port of the engine, is hermetically partitioned into a first air flow path (swirl port) and a second air flow path (main port) 5 by a partition portion (not shown). The swirl port is provided on one side of the intake port of the engine and generates an intake vortex in the combustion chamber of the cylinder of the engine. Further, the main port 5 is provided on the ground side in the vertical direction with respect to the swirl port among the intake ports of the engine. The housing 1 may be formed integrally with the cylinder head of the engine, or may be combined with the cylinder head of the engine after being manufactured separately from the cylinder head of the engine.

  The intake vortex flow control valve 2 is a swirl flow control valve that generates an intake vortex flow (swirl flow) in the combustion chamber of the cylinder by controlling the opening degree of the main port 5 and actively flowing an air flow in the swirl port. . The intake vortex control valve 2 has a valve shaft 15 that is drivingly connected to an output shaft 13 of a power transmission mechanism via a joint (torque transmission component) 14, and moves to rotate integrally with the valve shaft 15. A valve body of an air flow path opening / closing control valve (air vortex control valve) that switches the opening area of the main port 5 to at least two stages of a valve fully open position and a valve fully closed position. ing. Note that both end portions of the valve shaft 15 in the axial direction are rotatably supported by the bearing portions of the housing 1 via bearing components (for example, ball bearings) 16 and 17.

  As shown in FIG. 5A, the intake vortex flow control valve 2 is driven by the electric motor 4 (motor output shaft torque in the valve closing operation direction (forward rotation direction)) at the time of engine start or idle operation. The valve is driven to close in the valve closing operation direction (from the valve fully open position toward the valve fully closed position). Further, the intake vortex control valve 2 is configured so that the driving force of the electric motor 4 (valve opening operation) is shown in FIG. 5 (b) when the engine is in the middle / high speed rotation range (engine speed is 2500 rpm or more, for example). The valve is driven to open in the valve opening operation direction (from the valve fully closed position to the valve fully open position) by the direction (reverse direction motor output shaft torque) and the urging force (spring force) of the coil spring. In addition, when the engine is in a low speed rotation range (engine speed is about 2000 rpm, for example), the intake vortex control valve 2 may be operated in a half-open state by the motor output shaft torque.

  A rotation angle limiting member 19 is integrally provided on the outer periphery of the joint 14 mounted between the output shaft 13 of the power transmission mechanism and the valve shaft 15 of the intake vortex flow control valve 2. When the intake vortex control valve 2 is closed to the valve fully closed position, the rotation angle restricting member 19 is directly or indirectly connected to a fully closed mechanical stopper (fully closed valve stopper: not shown). When the intake valve vortex control valve 2 opens to the fully open position, the fully open stopper (not shown) directly or directly contacted with the fully open stopper (not shown) or A fully open stopper portion (not shown) that is indirectly contacted and locked is integrally formed. The two fully-closed and fully-open valve stoppers are integrally formed on the inner peripheral portion of the cylindrical wall portion 20 that is integrally provided on the outer wall portion of the housing 1.

  In this embodiment, a direct current (DC) motor that is energized and controlled by the ECU is employed as the electric motor 4. The electric motor 4 is electrically connected to a battery mounted on the vehicle via a motor drive circuit electronically controlled by the ECU. The electric motor 4 is a brushed DC motor constituted by a rotor (armature) integrated with the motor shaft 11, a stator (field) disposed opposite to the outer peripheral side of the rotor, and the like. Instead of the brushed DC motor, a brushless DC motor or an alternating current (AC) motor such as a three-phase induction motor may be used. Moreover, you may use a rotary solenoid instead of a motor as a motive power source.

  The power transmission mechanism is configured by a gear reduction mechanism 6 that reduces the rotational speed of the motor shaft 11 of the electric motor 4 so as to be a predetermined reduction ratio. The gear reduction mechanism 6 includes a worm gear 21 fixed to the motor shaft 11 of the electric motor 4, an intermediate gear 22 that meshes with the worm gear 21, and a final gear (hereinafter referred to as an output gear) 23 that meshes with the intermediate gear 22. It is configured. Here, the intermediate gear 22 includes a helical gear (or worm wheel) 24 that meshes with the worm gear 21, and an output spur gear 25 that is disposed on the same axis as the helical gear 24.

  Between the helical gear 24 and the output spur gear 25, an impact absorbing member (not shown) that rotates together with the gears 24 and 25 is disposed. The impact absorbing member has an elastic member (rubber material) and the like. In the case where torque transmission acts shockfully, the impact absorbing member, for example, at the moment when the intake vortex control valve 2 is fixed at the fully closed position of the valve, due to the torsional action that deforms the elastic member, the worm gear 21. It has the function of relaxing the impact load transmitted to the worm gear 21 and preventing the worm gear 21 from being tightened. Further, the helical gear 24 and the output spur gear 25 are rotatably supported on the outer periphery of the intermediate shaft 12 arranged perpendicular to the axial direction of the motor shaft 11 constituting the worm gear shaft. Both end portions of the intermediate shaft 12 are press-fitted and fixed to a housing 7 that forms a gear housing chamber (rotating body housing chamber) 26 in which each gear constituting the gear reduction mechanism 6 is rotatably housed.

  Next, the structure of the output gear 23 of the gear reduction mechanism 6 of the present embodiment will be briefly described with reference to FIGS. Here, FIG. 3 and FIG. 4 are diagrams showing the structure of the output gear 23.

  First, in the gear reduction mechanism 6 of the present embodiment, an output shaft 13 that extends straight in the axial direction is disposed so as to cross the gear housing chamber 26. Both ends of the output shaft 13 in the axial direction correspond to the shafts of the power transmission mechanism of the present invention, and are supported by the bearings of the housing 7 through the bearing parts 27 and 29 so as to be slidable in the rotational direction. Has been. As shown in FIGS. 1 and 2, one end of the output shaft 13 in the axial direction (the lower end in the drawing) protrudes outside the housing 7 constituting the actuator case, and controls the intake vortex flow through the joint 14. Drive connected to the valve shaft 15 of the valve 2.

  Next, the output gear 23 of the present embodiment is configured by two first and second rotating bodies 31 and 32 disposed so as to surround the periphery of the output shaft 13. These first and second rotating bodies 31 and 32 are integrated within the operating range of the intake vortex control valve 2 from the valve fully open position (operation start position) to the valve fully closed position (operation stop position). It is configured to rotate. Here, the torsion coil spring 9 is accommodated in the spring accommodating space 33 formed between the two first and second rotating bodies 31 and 32 so as to be elastically deformable.

  Here, the valve holding mechanism of the present embodiment has a housing 7 in which a gear housing chamber 26 is formed, and a torsion coil spring (load applying means) 9 corresponding to the frictional force applying means of the present invention. Yes. As shown in FIG. 3, the housing 7 has two first and second axial position restricting members 34 and 35 that are arranged to face each other with a predetermined axial gap (gear housing chamber 26) therebetween. Is formed. The opposing wall surfaces of the first and second axial position restricting members 34 and 35 on the gear housing chamber side are in the axial direction of the two first and second rotating bodies 31 and 32 and the output shaft 13 with respect to the housing 7. First and second restricting surfaces 36 and 37 for restricting the relative displacement amount are provided.

  In addition, the first restricting surface 36 restricts (locks) the rotation operation of the second rotating body 32, so that the first rotating body 31 is displaced relative to the second rotating body 32 when the first rotating body 31 is relatively displaced. It has a function as a first restricting portion that restricts the maximum displacement. Further, the second restricting surface 37 restricts (locks) the rotation operation of the second rotating body 32, and the second rotating body 32 moves when the second rotating body 32 is displaced relative to the first rotating body 31. It has a function as a 2nd control part which controls the maximum displacement amount.

  The first rotating body 31 is disposed on the motor side (power source side) on the power transmission path of the gear reduction mechanism 6, and has a double cylindrical first cylindrical portion 41, 42 and the first cylindrical portion 41. , 42 is connected to the first annular plate 43. On the other hand, the second rotating body 32 is disposed on the valve side (moving body side) on the power transmission path of the gear reduction mechanism 6, and has double cylindrical second cylindrical portions 51, 52 and these second cylindrical portions. It has the 2nd annular plate 53 which connects 51,52.

  The first cylindrical portion 41 of the first rotating body 31 is an outer diameter side cylindrical portion disposed on the outer diameter side in the radial direction with respect to the first cylindrical portion 42. On the outer periphery of the first cylindrical portion 41, a plurality of convex teeth 44 are formed in the entire circumferential direction. These convex teeth 44 form an input spur gear that meshes with the output spur gear 25 of the intermediate gear 22. The first cylindrical portion 41 has a part in the circumferential direction as an opening 60, and a first torque for applying a set torque to the torsion coil spring 9 on both sides in the circumferential direction of the opening 60. Spring hooks 61 and 62 are provided. The first spring hooks 61 and 62 are preferably disposed on the same circumference centered on the axis of the output shaft 13 and facing each other in the circumferential direction. Further, the first cylindrical portion 42 is an inner diameter side cylindrical portion disposed on the inner diameter side in the radial direction with respect to the first cylindrical portion 41. A spiral first screw 45 is formed on the entire inner circumference of the first cylindrical portion 42 in the axial direction.

A first spring seat portion (first seat portion) 63 that receives the spring load in the axial direction of the torsion coil spring 9 is provided on the end surface of the first annular plate 43 on the spring accommodating space side. Further, the end surface of the first annular plate 43 opposite to the spring accommodating space side is provided integrally with the housing 7 when the first rotating body 31 is relatively displaced with respect to the second rotating body 32. A first contact surface 64 capable of contacting the first restriction surface 36 of the first axial position restriction member 34 is provided. In the present embodiment, since the annular end portion of the first cylindrical portion 42 facing the bearing component 27 protrudes toward the bearing component side, the first contact surface 64 is provided at the annular end portion.
Here, between the first restricting surface 36 of the first axial position restricting member 34 of the housing 7 and the first contact surface 64 of the first annular plate 43 of the first rotating body 31, the valve is opened from the fully opened position. Within the operating range of the intake vortex control valve 2 up to the fully closed position, a predetermined (minimum) first clearance 65 required for the first rotating body 31 to rotate in the gear housing chamber 26 is formed. Has been.

  The second cylindrical portion 51 of the second rotating body 32 is an outer diameter side cylindrical portion disposed on the outer diameter side in the radial direction with respect to the second cylindrical portion 52. A spring accommodating space 33 is formed between the inner peripheral surface of the second cylindrical portion 51 and the outer peripheral surfaces of the first cylindrical portion 42 and the second cylindrical portion 52 of the first rotating body 31. Further, the first rotating body 31 relatively rotates around the second rotating body 32 between the outer peripheral surface of the second cylindrical portion 51 and the inner peripheral surface of the first cylindrical portion 41 of the first rotating body 31. A predetermined (minimum) clearance 54 is formed. The second cylindrical portion 51 has a portion in the circumferential direction that is an opening 70, and second spring hooks 71 and 72 are provided on both sides of the opening 70 in the circumferential direction. The second spring hook 71 is configured to apply an axial valve holding torque to the torsion coil spring 9 between the second spring hook 71 and the first spring hook 62 of the first rotating body 31. The second spring hooks 71 and 72 are preferably arranged on the same circumference centered on the axis of the output shaft 13 and facing each other in the circumferential direction.

  The second cylindrical portion 52 is an inner diameter side cylindrical portion disposed on the inner diameter side in the radial direction with respect to the second cylindrical portion 51. The output shaft 13 of the gear reduction mechanism 6 is press-fitted and integrated with the inner periphery of the second cylindrical portion 52. As a result, the second rotating body 32 is coupled to the output shaft 13 so as to be able to transmit power, thereby rotating integrally with the output shaft 13 and the two first and second axial directions of the housing 7. The position regulating members 34 and 35 can be relatively displaced integrally with the output shaft 13. A spiral second screw 55 that is screw-coupled to the first screw 45 of the first rotating body 31 is formed on the entire outer periphery of the second cylindrical portion 52 in the axial direction.

  A second spring seat portion (second seat portion) 73 that receives the spring load in the axial direction of the torsion coil spring 9 is provided on the end surface of the second annular plate 53 on the spring accommodating space side. Note that the first spring seat 63 of the first rotating body 31 and the second spring seat 73 of the second rotating body 32 are arranged to face each other with an axial gap therebetween, and the first spring of the first rotating body 31 is arranged. The torsion coil spring 9 may be disposed in the axial clearance (spring accommodating space 33) between the seat 63 and the second spring seat 73 of the second rotating body 32.

Further, when the second rotating body 32 is displaced relative to the second axial position restricting member 35 of the housing 7 on the end surface of the second annular plate 53 opposite to the spring accommodating space side, A second abutment surface 74 that can abut on the second regulating surface 37 of the axial position regulating member 35 is provided. In the present embodiment, an annular end facing the bearing component 29 of the second cylindrical portion 52 is provided, and a second contact surface 74 is provided at the annular end.
Here, between the second restricting surface 37 of the second axial position restricting member 35 of the housing 7 and the second contact surface 74 of the second annular plate 53 of the second rotating body 32, the valve is opened from the fully opened position. Within the operating range of the intake vortex control valve 2 up to the fully closed position, a predetermined (minimum) second clearance 75 necessary for the second rotary body 32 to rotate in the gear housing chamber 26 is formed. Has been.

  With the above-described structure, the second rotating body 32 of the output gear 23 is always drivingly connected (coupled) to the valve shaft 15 of the intake vortex control valve 2 via the output shaft 13 and the joint 14. The motor output shaft torque drives the valve shaft 15 of the intake vortex control valve 2 in the valve fully closed operation direction, and the fully closed stopper portion of the rotation angle limiting member 19 provided integrally with the joint 14 becomes the fully closed valve stopper. When the rotation operation of the intake vortex control valve 2 is restricted (locked) at the valve fully closed position, the rotation operation of the second rotating body 32 itself is also restricted (locked). .

  Further, since the first rotating body 31 of the output gear 23 has the first screw 45 that is screw-coupled with the second screw 55 of the second rotating body 32, the rotation operation of the second rotating body 32 is restricted (locked). ), When it is rotationally driven by the motor output shaft torque of the electric motor 4, it is relatively rotated with respect to the second rotating body 32 and at the same time is relatively displaced to one side in the axial direction with respect to the second rotating body 32. Is configured to do. The second rotating body 32 of the output gear 23 is relatively displaced to the other side in the axial direction with respect to the first rotating body 31 when the first rotating body 31 rotates relative to the second rotating body 32. It is configured as follows.

  The torsion coil spring 9 corresponds to the frictional force applying means of the present invention and is disposed on the power transmission path of the gear reduction mechanism 6 to transmit power to the two first and second rotating bodies 31 and 32. Combined as possible. The torsion coil spring 9 is provided around the output shaft 13 of the gear reduction mechanism 6 (in particular, the radii of the first and second cylindrical portions 41 and 51 of the two first and second rotating bodies 31 and 32 of the output gear 23). At least one of the first and second restricting surfaces 36 and 37 of the two first and second axial position restricting members 34 and 35 of the housing 7. It has a function as a valve holding mechanism with the first restricting surface 36.

  In addition, the torsion coil spring 9 has two first rotating bodies 31 when the first rotating body 31 rotates relative to the second rotating body 32 only when the operation of the intake vortex control valve 2 is stopped (when the intake vortex flow control valve 2 is fully closed). The first rotary body 31 is moved in the rotational direction of the first rotary body 31 between the first and second rotary bodies 31 and 32, so that the first rotary body 31 is moved relative to the first spring seat 63 of the first rotary body 31. 1 A function as a first spring load applying means for applying an axial spring load (holding torque) in a direction to be pressed against the regulating surface 36 and a second spring seat portion 73 of the second rotating body 32, a second It also has a function as a second spring load applying means for applying an axial spring load (holding torque) in the direction in which the rotating body 32 is pressed against the second regulating surface 37.

  The torsion coil spring 9 includes an inner circumference of the second cylindrical portion 51 of the second rotating body 32 and outer circumferences of the first and second cylindrical portions 42 and 52 of the two first and second rotating bodies 31 and 32. The cylindrical coil portion 90 is disposed in the spring accommodating space 33 formed between the two. The cylindrical coil portion 90 is formed on the output shaft 13 so as to spirally surround the first and second cylindrical portions 42 and 52 of the two first and second rotating bodies 31 and 32 in the spring accommodating space 33. Arranged along the axial direction. Then, on the both sides in the axial direction of the cylindrical coil portion 90 of the torsion coil spring 9, the first and second spring seat portions 63 and 73 of the two first and second rotating bodies 31 and 32 are respectively held (contacted). A pair of first and second coil terminals 91 and 92 are provided.

  The first coil terminal 91 is formed in an L shape, and is bent at a substantially right angle from one end portion (end portion on the motor side (power source side)) in the axial direction of the cylindrical coil portion 90 to the outer diameter side in the radial direction. It has been. This first coil terminal 91 is within the operating range of the intake vortex control valve 2 from the fully open position of the valve to the fully closed position of the valve, and the first spring hook 61 of the first rotating body 31 (or of the second rotating body 32). The second spring hook 71 is locked (held). Further, the first coil terminal 91 is locked (held) to the second spring hook 71 of the second rotating body 32 when the first rotating body 31 rotates relative to the second rotating body 32.

The second coil terminal portion 92 is formed in an L shape, and is substantially perpendicular to the radially outer diameter side from the other end portion in the axial direction of the cylindrical coil portion 90 (the end portion on the valve side (moving body side)). It is bent. The second coil terminal 92 is always locked (held) to the first spring hook 62 of the first rotating body 31 (or the second spring hook 72 of the second rotating body 32).
Therefore, the torsion coil spring 9 is configured such that when the first rotating body 31 relatively rotates with respect to the second rotating body 32, the first rotating body 31 is moved between the two first and second rotating bodies 31 and 32. By being twisted in the rotational direction, torsional elastic force in the opposite direction to the rotational direction of the first rotating body 31 is accumulated, and at the same time, against the first spring seat 63 of the first rotating body 31. A spring load in the axial direction is generated in the direction in which the first rotating body 31 is pressed against the first regulating surface 36, and the second rotating body 32 is second regulated with respect to the second spring seat 73 of the second rotating body 32. An axial spring load is generated in the direction of pressing against the surface 37.

  Here, the intake vortex generator for an internal combustion engine of the present embodiment converts the rotation angle (valve opening) of the intake vortex control valve 2 into an electrical signal (valve opening signal), and the intake vortex control valve 2 A non-contact type valve opening detection device is provided that outputs to the ECU whether the intake vortex control valve 2 is fixed at the fully open position, or how much the intake vortex control valve 2 is open. ing. This valve opening degree detection device is constituted by a permanent magnet (magnet) provided on a joint 14 fixed to the output shaft 13 of the intake vortex control valve 2, and a valve opening degree sensor that forms a magnetic circuit together with this magnet. ing. The valve opening sensor is configured by a pair of yokes (magnetic bodies) that are arranged to face the magnet and magnetized by the magnets, and a Hall IC that is arranged in a magnetic detection gap formed between the yokes. . The Hall IC is an IC (integrated circuit) in which a Hall element (non-contact type magnetic detection element) and an amplifier circuit are integrated, and the magnetic flux density passing through the magnetic detection gap (the magnetic flux density interlinked with the Hall IC). ) Is output.

  Here, the ECU is provided with a microcomputer having a well-known structure configured to include functions such as a CPU for performing control processing and arithmetic processing, various programs, and a storage device (memory such as ROM and RAM) for storing data. It has been. This ECU controls the rotational motion of the electric motor 4 by adjusting the power supplied to the electric motor 4 based on a control program stored in the memory when the ignition switch is turned on (IG / ON). Control unit. The ECU detects the engine rotation speed by a sensor signal such as a crank angle sensor (not shown) at the time of starting the engine or idling, and supplies electric power to the electric motor 4 in accordance with the engine rotation speed to intake the vortex control valve. The intake vortex control valve 2 is driven to close so that 2 is fully closed. Specifically, when the intake vortex control valve 2 is closed (fully closed) from the fully open position to the fully closed position (including the valve holding state), the timing chart of FIG. As shown, first, a motor drive current (for example, a large current in the forward rotation direction) is supplied to the electric motor 4.

  Then, after detecting the fully closed state (valve fully closed position) of the intake vortex control valve 2 by the valve opening sensor, the motor drive current (for example, forward rotation direction) is continuously supplied until a predetermined time elapses. Large current). Thereafter, the relative displacement and rotation of the first rotating body 31 with respect to the second rotating body 32 of the output gear 23 are changed to the output gear restricting position (the output gear 23 at the first restricting surface 36 of the first axial position restricting member 34). A position sensor (touch) that detects a change in motor driving current to the electric motor 4 or a relative displacement position of the first rotating body 31. The supply of the motor drive current to the electric motor 4 is stopped at the time point confirmed by the sensor or the like. When the supply of the motor drive current to the electric motor 4 is stopped and the electric motor 4 is turned off, the two first and second rotating bodies 31 and 32 of the output gear 23 are thrust at the output gear restriction position. If locking (holding) cannot be performed, a very small current (for example, a small current in the forward rotation direction) is continuously supplied to the electric motor 4.

  Further, the ECU detects the engine rotation speed during steady operation of the engine, supplies electric power to the electric motor 4 according to the engine rotation speed, and the intake vortex control valve 2 is fully opened. 2 is opened. Specifically, when the intake vortex control valve 2 is opened from the fully closed position (including the valve holding state) to the fully opened position (fully opened), the timing chart of FIG. As described above, first, a motor drive current (for example, a large current in the reverse direction) is supplied to the electric motor 4. When the fully open state (valve fully open position) of the intake vortex control valve 2 is detected by the valve opening sensor, the supply of the motor drive current to the electric motor 4 is stopped.

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

  First, in the state where the motor drive current is not supplied to the armature coil built in the electric motor 4, the output shaft 13 of the gear reduction mechanism 6 and the valve shaft 15 of the intake vortex control valve 2 are urged by the biasing force of the coil spring. The fully open stopper portion of the rotation angle limiting member 19 provided integrally with the joint 14 is engaged with the fully open valve stopper, and the intake vortex control valve 2 fully opens (opens) the main port 5. At this time, the torsion coil spring 9 accommodated between the output gear 23 of the gear reduction mechanism 6, particularly the two first and second rotating bodies 31, 32, has a pair of first, Since the second coil terminals 91 and 92 are respectively engaged with the first spring hooks 61 and 62 of the first rotating body 31, the torque of the cylindrical coil portion 90 of the torsion coil spring 9 (the torque of the torsion coil spring 9). ) Is only the “set torque” necessary to cause the rotation operation of the first rotation body 31 to follow the rotation operation of the second rotation body 32.

  Here, at the time of engine start or idle operation, a motor drive current (a large current in the forward direction) is applied to the armature coil of the electric motor 4 so that the valve position (valve opening) of the intake vortex control valve 2 is fully closed. ) Is supplied. When the armature coil of the electric motor 4 is energized, the motor shaft 11 starts to rotate. The rotational output of the electric motor 4 is transmitted from the worm gear 21 fixed to the motor shaft 11 to the helical gear 24 of the intermediate gear 22, from the helical gear 24 to the output spur gear 25 via an impact absorbing member (elastic member or the like), Transmission is sequentially performed from the output spur gear 25 of the intermediate gear 22 to the convex teeth (input spur gear) 44 of the first rotating body 31 of the output gear 23.

  The driving force (motor output shaft torque) of the electric motor 4 transmitted from the first rotating body 31 to the second rotating body 32 through the torsion coil spring 9 is transmitted from the second rotating body 32 to the gear reduction mechanism 6. It is transmitted to the output shaft 13. The motor output shaft torque transmitted to the output shaft 13 of the gear reduction mechanism 6 is transmitted to the valve shaft 15 of the intake vortex control valve 2 via the joint 14. As a result, the intake vortex control valve 2 rotates about the rotation center axis (axis) of the valve shaft 15 against the biasing force of the coil spring, so that the valve position of the intake vortex control valve 2 is the valve fully open position. To the valve fully closed position in the valve closing operation direction (forward rotation direction). When the fully closed stopper portion of the rotation angle limiting member 19 is locked to the fully closed valve stopper, the rotation operation of the intake vortex control valve 2 and the valve shaft 15 in the valve closing operation direction (forward rotation direction) is restricted ( Locked). At this time, the main port 5 is fully closed (closed).

  As a result, the intake air filtered by the air cleaner flows into the intake port of the engine via the intake passage of the engine intake pipe. At this time, since the main port 5 is closed by the intake vortex flow control valve 2, a one-side ventilation state of only the swirl port is formed. As a result, a lateral vortex flow (swirl flow) is generated in the intake air in the cylinder of the engine. Due to the generation of the intake vortex, the combustion speed in the cylinder is accelerated, the combustion efficiency is improved, and the fuel efficiency and emission during idling are improved.

  Here, as described above, the rotation of the intake vortex control valve 2 and the valve shaft 15 is restricted (locked) by the fully closed stopper portion of the rotation angle limiting member 19 being locked to the fully closed valve stopper. Then, the rotation operation of the output shaft 13 of the gear reduction mechanism 6 is also restricted (locked). Thereby, the rotation operation of the second rotating body 32 fixed to the outer periphery of the output shaft 13 of the gear reduction mechanism 6 is also restricted (locked). At this time, as shown in FIG. 5A, the ECU detects that the valve position of the intake vortex control valve 2 is the valve fully closed position by the valve opening sensor, but the armature coil of the electric motor 4 is used as it is. The motor drive current (for example, large current in the forward direction) is continuously supplied to the motor.

  As described above, the motor output shaft torque of the output gear 23 is continuously applied to the output gear 23 by the electric motor 4 in a state where the rotation operations of the output shaft 13 and the second rotating body 32 are restricted (locked). The one rotating body 31 is rotated in the forward rotation direction. That is, since the first rotating body 31 rotates relative to the output shaft 13 and the second rotating body 32 in the valve closing operation direction (forward rotation direction), as shown in FIG. The first spring hooks 61 and 62 move in the left rotation direction in the drawing relative to the second spring hooks 71 and 72 of the second rotating body 32. Then, since the pair of first and second coil terminals 91 and 92 of the torsion coil spring 9 are displaced so as to narrow the circumferential interval from the state of being opposed to each other in the circumferential direction, the cylinder of the torsion coil spring 9 is arranged. The coil unit 90 is twisted up in the rotation direction of the first rotating body 31.

  During the twisting operation of the cylindrical coil portion 90 of the torsion coil spring 9, a screw mechanism constituted by the first screw 45 of the first rotating body 31 and the second screw 55 of the second rotating body 32, The first rotating body 31 is relatively displaced to one side in the axial direction (upward in the drawing) with respect to the second rotating body 32 whose rotation operation is restricted (locked), and at the same time, the first rotating body 31 Since the two-rotor 32 is relatively displaced to the other side in the axial direction (downward in the drawing), the overall height (size in the axial direction) of the structure of the output gear 23 constituted by the two first and second rotors 31 and 32 is growing.

  When the intake vortex flow control valve 2 is operated in the valve closing operation direction, the intake vortex flow control valve 2 is formed between the first restriction surface 36 of the first axial position restriction member 34 and the first contact surface 64 of the first rotating body 31. The first clearance 65 becomes 0 (zero). Therefore, the first contact surface 64 of the first rotating body 31 contacts the first restricting surface (output gear restricting position) 36 of the first axial position restricting member 34, and the first rotation with respect to the second rotating body 32 is performed. The relative displacement of the body 31 in one axial direction is restricted by the maximum displacement amount (full lift amount). Further, when the intake vortex flow control valve 2 is operated in the valve closing operation direction, it is formed between the second restriction surface 37 of the second axial position restriction member 35 and the second contact surface 74 of the second rotating body 32. The second clearance 75 becomes 0 (zero). Accordingly, the second abutting surface 74 of the second rotating body 32 abuts on the second restricting surface (output gear restricting position) 37 of the second axial position restricting member 35, and the second rotation with respect to the first rotating body 31 is performed. The relative displacement of the body 32 toward the other side in the axial direction is restricted by the maximum displacement amount (full lift amount).

  At this time, since the cylindrical coil portion 90 of the torsion coil spring 9 is twisted up in the rotation direction of the first rotating body 31, the axial direction of the output gear 23 is added to the cylindrical coil portion 90 of the torsion coil spring 9. The spring load is generated. As a result, the one end portion of the cylindrical coil portion 90 of the torsion coil spring 9 in the axial direction and the first coil terminal 91 are in contact with the first spring seat portion 63 of the first rotating body 31. A spring load is applied in the direction in which the first contact surface 64 is pressed against the first regulating surface 36, and at the same time, the other end portion of the torsion coil spring 9 in the axial direction of the cylindrical coil portion 90 and the second coil terminal 92 are rotated in the second rotation. A spring load is applied to the second spring seat portion 73 of the body 32 in a direction in which the second contact surface 74 of the second rotating body 32 is pressed against the second restriction surface 37.

  As a result, the sliding torque (frictional force) due to the thrust lock of the first rotating body 31 between the first contact surface 64 of the first rotating body 31 and the first restricting surface 36 of the first axial position restricting member 34. Between the second contact surface 74 of the second rotating body 32 and the second restricting surface 37 of the second axial position restricting member 35, and a sliding torque (frictional force) due to the thrust lock of the second rotating body 32. ) Is given. Therefore, the rotation operation of the intake vortex control valve 2 coupled to the output gear 23 via the output shaft 13, the joint 14, and the valve shaft 15 is held (locked) at the valve fully closed position (valve holding state). As shown in FIG. 5 (a), the ECU is further restricted in the thrust direction operation at the output gear restricting position of the two first and second rotating bodies 31, 32 of the output gear 23. At the time, or after a predetermined time has elapsed since the detection of the fully closed position of the intake vortex control valve 2, the supply of the motor drive current (for example, large current in the forward direction) to the armature coil of the electric motor 4 is stopped. At this time, the torque of the cylindrical coil portion 90 of the torsion coil spring 9 (torque of the torsion coil spring 9) is (“set torque” + “twisted torque”).

  In this embodiment, when the engine is started or idling, the armature coil of the electric motor 4 is energized and the valve opening (valve position) of the intake vortex control valve 2 is fully closed (valve fully closed position). ). That is, the normally open intake vortex control valve 2 is driven to close by the motor actuator 3. On the contrary, the armature coil of the electric motor 4 may be energized and controlled so that the valve opening (valve position) of the intake vortex control valve 2 is fully open (valve fully open position). In this case, a normally closed intake flow control valve is obtained.

[Features of Example 1]
As described above, in the gear reduction mechanism 6 of the motor actuator 3 of this embodiment, as shown in FIGS. 2 and 3, the thrust direction of the output gear 23 of the gear reduction mechanism 6 (the axial direction of the output shaft 13). In addition, in order to smoothly rotate the output gear 23 and reduce loss due to sliding, it is usual to provide a certain amount of first and second clearances 65 and 75. According to the gear reduction mechanism 6 of the present embodiment, when the intake vortex control valve 2 is in an operating state, the total height of the output gear 23 is set to a height that can secure the first and second clearances 65 and 75 described above. Has been.

  Here, when the intake vortex control valve 2 is driven to close by the motor output shaft torque of the electric motor 4 and the rotation operation of the intake vortex control valve 2 in the valve closing operation direction is restricted at the valve fully closed position, At the same time as the rotation of the vortex control valve 2 is stopped, the rotation of the second rotating body 32 of the output gear 23 is also restricted (locked). When the rotation operation of the second rotating body 32 of the output gear 23 is restricted (locked) when the intake vortex control valve 2 is fully closed, the first rotating body 31 rotates relative to the second rotating body 32. Therefore, the cylindrical coil portion 90 of the torsion coil spring 9 is twisted up between the two first and second rotating bodies 31 and 32. As a result, the two first and second rotating bodies 31 and 32 are provided to the cylindrical coil portion 90 of the torsion coil spring 9 with respect to the two first and second rotating bodies 31 and 32, and the first and second restrictions. A spring load is generated in the direction of pressing against the surfaces 36 and 37.

  Here, when the rotation operation of the intake vortex control valve 2 is restricted at the valve fully closed position, as described above, the two first and second rotating bodies 31 and 32 are relatively displaced to both sides in the axial direction. Therefore, the overall height of the structure of the output gear 23 is increased. As a result, the first clearance 65 in the thrust direction formed between the first contact surface 64 of the first rotating body 31 and the first restricting surface 36 becomes 0 (zero), and the second rotating body 32 The second clearance 75 in the thrust direction formed between the second contact surface 74 and the second restriction surface 37 becomes 0 (zero). Further, since the first rotating body 31 is pressed against the first regulating surface 36 by the axial spring load generated in the cylindrical coil portion 90 of the torsion coil spring 9, the sliding resistance of the first rotating body 31 of the output gear 23 is reduced. Becomes larger.

  Therefore, the rotation operation of the output gear 23 is restricted (locked), and the rotation operation of the intake vortex control valve 2 can be locked at the valve fully closed position. Thus, the first and second clearances 65 and 75 in the thrust direction are eliminated, and the output gear 23 is locked, so that the self-locking property (non-energized reverse rotation torque) of the motor actuator 3 can be increased, and the intake air In the operating state of the vortex control valve 2, the first and second clearances 65 and 75 are ensured, so that the operating efficiency of the gear reduction mechanism 6 of the motor actuator 3 is not reduced.

  As described above, in the gear reduction mechanism 6 of the motor actuator 3 of the present embodiment, as shown in FIGS. 3 and 4, the two first and second only when the intake vortex control valve 2 is fully closed. Since the frictional force is applied to at least one of the rotating bodies 31 and 32, the intake vortex control valve 2 is held (locked) at the valve fully closed position. As a result, as shown in FIG. 8B, the valve holding force of the valve holding mechanism in the valve fully closed position (valve holding state) of the intake vortex control valve 2 can be improved, and the intake vortex control valve 2 can be improved. It is possible to prevent a reduction in the operating efficiency of the gear speed reduction mechanism 6 of the motor actuator 3 during the operation of.

  According to the gear reduction mechanism 6 of the motor actuator 3 of the present embodiment, the first and second clearances 65 and 75 in the thrust direction are eliminated, and the output gear 23 is locked in both rotational directions of the output gear 23 (valve closing operation). Direction (valve opening operation direction) is only one direction (valve closing operation direction), and the other direction (valve opening operation direction) operates in a direction in which the height of the structure of the output gear 23 decreases. However, the large holding torque of the intake vortex control valve 2 is required in one of the two positions of the valve fully open position and the valve fully closed position (valve fully closed position), so that the output gear 23 is locked. There is no problem if the rotational direction of the intake vortex control valve 2 requiring holding torque is aligned. That is, the threading direction of the screw mechanism constituted by the first screw 45 of the first rotating body 31 and the second screw 55 of the second rotating body 32 may be changed.

In the valve holding state in which the rotation operation of the intake vortex control valve 2 of this embodiment is held (locked) at the valve fully closed position, the torque relationship is expressed by the following equation (1).
[Equation 1]
"Necessary valve holding torque"
<"Torque of torsion coil spring 9"
<"Reverse idling torque of worm gear 21" + "Sliding torque by thrust lock"

  Here, in the gear reduction mechanism 6 of the motor actuator 3 of the present embodiment, the torsion coil spring 9 is used as the friction force applying means. However, the friction force applying means is not limited to the torsion coil spring 9. The structure of Example 1 can be configured using other elastic members (plate springs, rubbers). For example, when the first rotating body 31 and the second rotating body 32 are coupled using rubber, and the rotation operation of the second rotating body 32 is restricted (locked), the first rotating body 32 is first What is necessary is just to make it the structure where rubber | gum is twisted between the two 1st, 2nd rotary bodies 31 and 32 by rotating the rotary body 31 relatively.

  Although not mentioned in the detailed structure of the first embodiment, since the output gear 23 and the torsion coil spring 9 cannot be assembled in the configuration as it is, the output gear is actually as shown in FIG. After the first rotating body 31 or the second rotating body 32, which is a constituent element of 23, is divided into two or more parts, the torsion coil spring 9 is accommodated between the first and second rotating bodies 31 and 32. Thus, although it is necessary to assemble the output gear 23 so as to surround the output shaft 13, the effect of the first embodiment is not reduced.

  As a specific example, as shown in FIG. 6, the second rotating body 32 is divided into two parts, for example, a second cylindrical part 51 in which a second annular plate 53 is integrated and a second cylindrical part 52. . Next, the output shaft 13 is fixed to the inner periphery of the second cylindrical portion 52 by press fitting. Next, the 2nd cylindrical part 52 which press-fitted the output shaft 13 with respect to the 1st rotary body 31 incorporating the torsion coil spring 9 is assembled | attached along a screw mechanism. Finally, with the second cylindrical portion 51 positioned, the output shaft 13, the output gear 23, and the torsion coil spring 9 are integrally formed by press-fitting and fixing to the outer periphery of the second cylindrical portion 52. And

  FIG. 7 shows a second embodiment of the present invention, and FIG. 7 shows the structure of the intermediate gear.

  In the present embodiment, a valve holding mechanism (movement) that holds (locks) the intake vortex control valve 2 at the valve fully closed position on the intermediate gear 22 disposed on the power transmission path of the gear speed reduction mechanism 6 of the motor actuator 3. Body holding mechanism). Here, the intermediate gear 22 of the gear reduction mechanism 6 is constituted by two first and second rotating bodies 31 and 32 disposed with a slight gap so as to surround the periphery of the intermediate shaft 12. These first and second rotating bodies 31 and 32 are integrated within the operating range of the intake vortex control valve 2 from the valve fully open position (operation start position) to the valve fully closed position (operation stop position). It is configured to rotate. Here, the torsion coil spring 9 is accommodated in the spring accommodating space 33 formed between the two first and second rotating bodies 31 and 32 so as to be elastically deformable.

  The first rotating body 31 is disposed on the motor side (power source side) on the power transmission path of the gear reduction mechanism 6, and has a double cylindrical first cylindrical portion 41, 42 and the first cylindrical portion 41. , 42 is connected to the first annular plate 43. On the other hand, the second rotating body 32 is disposed on the valve side (moving body side) on the power transmission path of the gear reduction mechanism 6, and has double cylindrical second cylindrical portions 51 and 52, and these second cylindrical portions. A second annular plate 53 for connecting 51 and 52 and a second cylindrical portion 56 projecting downward from the second annular plate 53 in the figure are provided.

  A plurality of convex teeth 44 are formed in the entire circumferential direction on the outer periphery of the first cylindrical portion 41 of the first rotating body 31. These convex teeth 44 form a helical gear 24 that meshes with the worm gear 21 fixed to the motor shaft 11 of the electric motor 4. Further, a spiral first screw 45 is formed on the entire inner circumference of the first cylindrical portion 42 in the axial direction. A first spring seat portion (first seat portion) 63 and a first contact surface 64 are provided on both end surfaces of the first annular plate 43 in the plate thickness direction. Here, between the first restricting surface 36 of the first axial position restricting member 34 of the housing 7 and the first contact surface 64 of the first rotating body 31, the inside of the gear housing chamber 26 is located in the first rotating body 31. A predetermined (minimum) first clearance 65 necessary for the rotary operation of the is formed.

  The torsion coil spring 9 is accommodated between the inner peripheral surface of the second cylindrical portion 51 of the second rotating body 32 and the outer peripheral surfaces of the first cylindrical portion 42 and the second cylindrical portion 52 of the first rotating body 31. A spring accommodating space 33 is formed. Further, the second cylindrical portion 52 is disposed so as to surround the periphery of the intermediate shaft 12. The intermediate shaft 12 may be press-fitted and fitted to the inner periphery of the second rotating body 32 so that the second rotating body 32 and the intermediate shaft 12 may be integrated as separate parts, and both ends of the intermediate shaft 12 in the axial direction may be separated. The second rotating body 32 may be slidable in the rotational direction on the outer periphery of the intermediate shaft 12 with the portion fixed to the housing 7 by press fitting.

  A spiral second screw 55 that is screw-coupled to the first screw 45 of the first rotating body 31 is formed on the entire outer periphery of the second cylindrical portion 52 in the axial direction. A second spring seat portion (second seat portion) 73 and a second contact surface 74 are provided on both end surfaces of the second annular plate 53 in the plate thickness direction. Here, between the second restricting surface 37 of the second axial position restricting member 35 of the housing 7 and the second abutting surface 74 of the second rotating body 32, the inside of the gear housing chamber 26 is located in the second rotating body 32. A predetermined (minimum) second clearance 75 necessary for the rotary operation of the is formed. The second cylindrical portion 56 is disposed so as to surround the periphery of the intermediate shaft 12, similarly to the second cylindrical portion 52. On the outer periphery of the second cylindrical portion 56, a plurality of convex teeth 76 are formed in the entire circumferential direction. These convex teeth 76 form an output spur gear 25 that meshes with the output gear 23 of the gear reduction mechanism 6.

[Modification]
In this embodiment, the actuator of the present invention is applied to the motor actuator 3 that drives the intake vortex control valve 2 to close (or opens) the intake variable valve used in the variable intake device for the internal combustion engine. May be applied to a motor actuator that opens (or closes) the valve. Further, the throttle opening control device for an internal combustion engine that controls the amount of intake air taken into the combustion chamber of the cylinder of the engine by driving the electric motor of the actuator of the present invention in accordance with the depression amount of the accelerator pedal of the driver. The present invention may be applied to a motor actuator that controls the throttle opening corresponding to the rotation angle of the throttle valve used in the above.

  In addition, the moving body (valve such as a rotator) of the present invention is controlled by an intake control valve that controls the amount of intake air drawn into the combustion chamber of the engine, and an exhaust control that controls the amount of exhaust gas discharged from the combustion chamber of the engine. Valve, idle rotation speed control valve that controls the amount of intake air that bypasses the throttle valve, exhaust gas that controls the amount of exhaust gas recirculation that recirculates part of the exhaust gas discharged from the combustion chamber of the engine from the exhaust passage to the intake passage You may apply to a gas recirculation | reflux amount control valve (EGR control valve). In addition to the butterfly valve-type rotary valve as described above, the movable body of the present invention (valve such as a rotary body) can be a single-open rotary valve, a rotary valve, a poppet valve, or a shutter. The present invention may be applied to a valve of a type and a door type valve that is supported on only one side. The motor actuator of the present invention may be applied to a motor actuator that drives a moving body such as a passage switching door or an opening / closing door of a vehicle air conditioner. Further, the present invention may be applied to a motor actuator that drives a moving body such as a rotating body (rotor) of a fluid pumping machine (for example, a blower, a compressor, or a pump) that pressurizes and pumps a fluid such as gas or liquid.

FIG. 1 is a schematic diagram illustrating a schematic configuration of an intake vortex generator for an internal combustion engine (Example 1). (A), (b) is the front view and side view which showed the whole structure of the motor actuator (Example 1). (A) is AA sectional drawing of (b), (b) is sectional drawing which showed the structure of the output gear (Example 1). (A) is BB sectional drawing of (b), (b) is sectional drawing which showed the structure of the output gear (Example 1). (A) is the timing chart which showed the motor control method at the time of valve closing operation, (b) is the timing chart which showed the motor control method at the time of valve opening operation (Example 1). FIG. 3 is a cross-sectional view showing the structure of the output gear (Example 1). (Example 2) which is sectional drawing which showed the structure of the spur gear for output. (A) is the graph which showed the operating efficiency of the prior art, (b) is the graph which showed the operating efficiency of Example 1. FIG.

Explanation of symbols

1 Housing 2 Intake vortex control valve (moving body, valve body of intake vortex control valve)
3 Motor actuator 4 Electric motor (power source)
6 Gear reduction mechanism (power transmission mechanism)
7 Housing 9 Torsion coil spring (moving body holding mechanism, frictional force applying means, load applying means)
13 Output shaft 15 Valve shaft 22 Intermediate gear 23 Output gear (final gear)
26 Gear storage chamber (rotating body storage chamber)
31 First Rotating Body 32 Second Rotating Body 33 Spring Housing Space 34 First Axial Position Restricting Member 35 Second Axial Position Restricting Member 36 First Restricting Surface (Regulating Part)
37 2nd regulatory surface
45 1st screw 55 2nd screw 63 1st spring seat part (1st seat part)
64 1st contact surface 65 1st clearance 73 2nd spring seat part 74 2nd contact surface 75 2nd clearance

Claims (11)

(A) a power source that generates a driving force for driving the moving body;
(B) a power transmission mechanism for transmitting the driving force of the power source to the moving body;
(C) In an actuator comprising a moving body holding mechanism that holds the moving body at an operation stop position of the moving body,
The power transmission mechanism is arranged so as to surround an axis extending in the axial direction and the periphery of the shaft, and the operation of the mobile body from the operation start position of the mobile body to the operation stop position of the mobile body Within the range, it has two first and second rotating bodies that rotate integrally,
The first rotating body is disposed closer to the power source than the second rotating body on the power transmission path of the power transmission mechanism,
The second rotating body is disposed closer to the moving body than the first rotating body on the power transmission path of the power transmission mechanism,
The moving body holding mechanism is configured to stop at least one of the two first and second rotating bodies only when the moving body stops operating at the operation stop position of the moving body. A frictional force applying means for applying a frictional force to one of the rotating bodies,
The frictional force applying means is disposed on a power transmission path of the power transmission mechanism, and couples the two first and second rotating bodies so as to be able to transmit power. . The actuator according to claim 1, wherein
The first rotating body has a spiral first screw,
The actuator according to claim 2, wherein the second rotating body has a spiral second screw that is screw-coupled to the first screw. The actuator according to claim 1, wherein
The second rotating body has a spiral second screw, and is configured such that when the moving body stops operating, its rotating operation is restricted,
The first rotating body has a spiral first screw that is screw-coupled to the second screw, and is relative to the second rotating body when the rotation operation of the second rotating body is restricted. Is configured to rotate,
The two first and second rotating bodies are configured to be relatively displaced toward both sides in the axial direction when the first rotating body rotates relative to the second rotating body. An actuator characterized by. The actuator according to claim 3, wherein
The moving body holding mechanism regulates a maximum displacement amount of at least one of the two first and second rotating bodies when the two first and second rotating bodies are displaced relative to each other. Have a regulatory department,
The frictional force imparting means is configured so that the frictional force applying means is applied to at least one of the two first and second rotating bodies only when the operation of the moving body is stopped. An actuator having load applying means for applying a load in a direction in which at least one rotating body is pressed against the restricting portion. The actuator according to claim 4, wherein
The moving body holding mechanism has a housing in which a rotating body accommodation chamber is formed,
The actuator is characterized in that the two first and second rotating bodies are accommodated in the rotating body accommodating chamber so as to be rotatable relative to the housing. The actuator according to claim 5, wherein
The restricting portion is a restricting surface provided in the housing,
At least one of the two first and second rotating bodies has a contact surface that contacts the regulating surface of the housing,
Between the regulating surface of the housing and the contact surface of at least one of the two first and second rotating bodies, the rotating body housing chamber is disposed within the operating range of the moving body. An actuator, wherein a predetermined clearance necessary for at least one of the two first and second rotating bodies to rotate is formed. The actuator according to any one of claims 4 to 6,
The actuator according to claim 1, wherein the load applying means is a spring that is twisted in a rotation direction of the first rotating body when the first rotating body rotates relative to the second rotating body. The actuator according to any one of claims 4 to 6,
The actuator is characterized in that the load applying means is a rubber that is twisted in the rotation direction of the first rotating body when the first rotating body rotates relative to the second rotating body. The actuator according to any one of claims 1 to 8,
The two first and second rotating bodies constitute a final gear or an intermediate gear disposed on a power transmission path of the power transmission mechanism. The actuator according to any one of claims 1 to 9,
A housing that forms an intake passage communicating with the combustion chamber of the internal combustion engine;
The actuator according to claim 1, wherein the moving body is a valve body of an air flow rate control valve that controls an amount of air flowing from the intake passage into the combustion chamber by changing an opening area of the intake passage. The actuator according to any one of claims 1 to 9,
A housing that forms an intake passage communicating with the combustion chamber of the internal combustion engine;
The actuator is a valve body of an intake vortex control valve that generates a vortex in the air flowing into the combustion chamber from the intake passage by switching the opening area of the intake passage in two stages. .

Images