JP7323485B2 - Intake control device - Google Patents

Description

The present invention relates to an intake control device for an internal combustion engine.

Conventionally, a body having an intake passage, a shaft supported by the body, a valve body fixed to the shaft in the intake passage and increasing or decreasing the passage cross-sectional area of the intake passage according to the rotation of the shaft, and a gear lever fixed to the shaft. , and a closing direction spring that acts between the gear lever and the body to apply a turning force in the closing direction to the gear lever (see, for example, Patent Document 1).

The intake control device of Patent Document 1 further includes a default lever fixed to a shaft as a default mechanism that positions the valve disc between a fully open position and a fully closed position when no driving force is applied to the gear lever. It has an opening direction spring that provides a rotational force of . In this intake control device, both the closing direction spring and the opening direction spring are formed of coil springs, and both are arranged closer to the body than the gear lever.

JP 2018-105149 A

However, in the intake control device of Patent Document 1, both the closing direction spring and the opening direction spring are arranged closer to the body than the gear lever, so that they occupy a large space in the direction along the shaft. Furthermore, the closing direction spring is assembled in the intake control device with a biasing force applied in advance between the default lever and the gear lever, and is therefore difficult to assemble. As such, assembly requires complex jigs and processes.

SUMMARY OF THE INVENTION An object of the present invention is to provide an intake control device with a default mechanism that is particularly compact in size in the axial direction and is easy to assemble.

The intake control device of the present invention includes:
a first body having a first intake passage therein;
a first shaft rotatably supported by the first body;
a first valve body disposed in the first intake passage and attached to the first shaft for increasing or decreasing the passage cross-sectional area of the first intake passage as the first shaft rotates;
a rotating lever supported by the first shaft so as not to be mutually rotatable and imparting a rotational force to the first shaft;
a first biasing member and a second biasing member acting between the rotating lever and the first body to apply a rotational force to the rotating lever about the rotation axis of the first shaft;
Both the first biasing member and the second biasing member are coil springs formed by winding wire in a cylindrical shape,
One of the first biasing member and the second biasing member is a return spring that biases the rotating lever in a direction in which the first valve body reduces the cross-sectional area of the passage, and the other is the rotating lever. In the intake control device, wherein the first valve body is a default spring that biases the movement lever in the direction of increasing the cross-sectional area of the passage,
The first biasing member is arranged closer to the first valve body than the rotating lever in a first direction parallel to the rotation axis of the first shaft,
The second biasing member is arranged on the side opposite to the first valve body with respect to the rotating lever in the first direction,
Both the first biasing member and the second biasing member are arranged so that the center line of the cylindrical shape thereof overlaps the rotation axis of the first shaft,
The intake control device further comprises:
a second body having a second intake passage therein;
a second shaft rotatably supported by the second body;
a second valve body disposed in the second intake passage and attached to the second shaft for increasing or decreasing the passage cross-sectional area of the second intake passage as the second shaft rotates;
a reduction gear that is rotatably supported by the first body about a rotational axis parallel to the first direction and that transmits rotational force to the rotating lever;
The first body and the second body are fixed to each other such that the rotation axis of the first shaft and the rotation axis of the second shaft are arranged substantially on the same straight line,
When viewed from a direction parallel to a first reference line orthogonal to both the rotation axis of the first shaft and the rotation axis of the reduction gear, the first biasing member is provided in the first body and is arranged in the first direction. arranged so as to at least partially overlap the outer peripheral surface of the substantially cylindrical first shaft support portion that supports the shaft,
When viewed in a direction parallel to the first reference line, the second biasing member is provided on the second body to support the second shaft. are arranged so that the parts overlap,
The intake control device further comprises:
a tuning lever disposed closer to the first shaft than the second valve body of the second shaft and held by the second shaft so as not to be mutually rotatable with the second shaft;
a connecting mechanism that connects the rotating lever and the tuning lever to synchronize the movements of the first shaft and the second shaft about their rotation axes;
The first biasing member includes a first locking portion extending radially outward from the center line of the cylindrical shape of the first shaft support portion and locked to the first body; a second locking portion that extends and is capable of coming into contact with both the rotating lever and the first body;
The second biasing member includes a third locking portion extending radially outward from the center line of the cylindrical shape of the second shaft support portion and locked to the second body; a fourth locking portion that extends and is capable of coming into contact with both the tuning lever and the second body;
The first body includes a second contact portion that contacts the second locking portion,
The second body includes a fourth contact portion that contacts the fourth locking portion,
When viewed in the first direction, at least one of the second contact portion and the fourth contact portion is within a movable rotation range of any one of the rotating lever, the tuning lever, and the connecting mechanism. It is characterized by being arranged .

According to the present invention, the degree of freedom in arranging the first and second urging members, the rotating lever, etc. in the first direction is increased, so that it is possible to easily achieve miniaturization of the intake control device in the first direction. can be done.
Further, since the first biasing member is arranged so as to overlap the first shaft support portion, and the second biasing member is arranged so as to overlap the second shaft support portion, the first and second biasing members are provided. When the default mechanism is provided between the first and second bodies, the first and second urging members can be compactly arranged in the first direction.
In addition, the first to fourth locking portions of the rotating lever and the tuning lever and the first to fourth contacting portions that abut thereon are prevented from interfering with movable parts such as the rotating lever and the tuning lever. It can be divided into the 1st body side and the 2nd body side and distributed. As a result, the degree of freedom in the layout of each part can be improved, and the intake control device can be configured more compact in the first direction .

Another intake control device of the present invention comprises:
a first body having a first intake passage therein;
a first shaft rotatably supported by the first body;
a first valve body disposed in the first intake passage and attached to the first shaft for increasing or decreasing the passage cross-sectional area of the first intake passage as the first shaft rotates;
a rotating lever supported by the first shaft so as not to be mutually rotatable and imparting a rotational force to the first shaft;
a first biasing member and a second biasing member acting between the rotating lever and the first body to apply a rotational force to the rotating lever about the rotation axis of the first shaft;
Both the first biasing member and the second biasing member are coil springs formed by winding wire in a cylindrical shape,
The first biasing member is a return spring that biases the rotating lever in a direction in which the first valve body reduces the cross-sectional area of the passage, and the first biasing member moves the rotating lever to the first position. In an intake control device in which the valve body is a default spring that biases in the direction of increasing the passage cross-sectional area,
The first biasing member is arranged closer to the first valve body than the rotating lever in a first direction parallel to the rotation axis of the first shaft,
The second biasing member is arranged on the side opposite to the first valve body with respect to the rotating lever in the first direction,
Both the first biasing member and the second biasing member are arranged so that the center line of the cylindrical shape thereof overlaps the rotation axis of the first shaft,
a movable rotation range of the first shaft is set to 90 degrees or less,
the rotating lever is a lever gear driven by a reduction gear;
The reduction gear includes a large-diameter gear supported by the first body so as to be rotatable about a rotation axis parallel to the first direction, and non-rotatably arranged on the parallel rotation axis; Consists of small diameter gears,
The small-diameter gear is arranged closer to the first body than the large-diameter gear and meshes with the lever gear,
When viewed in a second direction parallel to a first reference line perpendicular to both the rotation axis of the first shaft and the rotation axis of the reduction gear, the first biasing member is provided on the first body and arranged so as to at least partially overlap the outer peripheral surface of a substantially cylindrical first shaft support portion that supports the first shaft;
The outer diameter of the cylindrical shape of the second biasing member is the difference between the sum of the diameter of the reference pitch circle of the lever gear and the diameter of the reference pitch circle of the small-diameter gear, and the diameter of the addendum circle of the large-diameter gear. smaller,
at least part of the second biasing member is arranged to overlap the large-diameter gear when viewed in the second direction;
The second biasing member includes a third engaging portion extending radially outward from the center of the cylindrical shape and engaged with the rotating lever, and a third engaging portion extending radially outwardly and engaging the rotating lever. a fourth locking portion capable of coming into contact with both the lever and the first body;
The fourth locking portion is arranged so as to overlap with the large-diameter gear when viewed in the second direction,
a positional relationship between the rotating lever and the first body when only biasing forces from the first biasing member and the second biasing member can act on the rotating lever; to the fully closed position, the default angle is 45 degrees or less, and
When viewed in the first direction, a first line segment connecting the rotation axes of the first and second shafts to the large-diameter gear side of the third engaging portion is defined as the rotation axes of the first and second shafts. The large-diameter gear is arranged outside a fan-shaped range expressed as a trajectory rotated by the default angle toward the large-diameter gear side.

According to this, when viewed in the second direction, the return spring is arranged so as to overlap the first shaft support portion of the first body, and the default spring is arranged so as to overlap the large-diameter gear to constitute the default mechanism. is made possible, the intake control device can be configured more compactly in the first direction.

FIG. 1A is a cross-sectional view of an intake control device according to an embodiment of the present invention, and FIG. 1B is a perspective view showing a first body side portion connected to a second body with the second body removed. be. FIG. 4 is a cross-sectional view showing a connecting portion of the first and second bodies; FIG. 4 is a perspective view showing a connecting portion of the first and second bodies with the first and second bodies removed; 4A is a perspective view showing the configuration of the first body related to the rotating lever, and FIG. 4B is a perspective view showing the configuration of the second body related to the tuning lever. FIG. 5A is a diagram showing the positional relationship between the reduction gear and the tuning lever when viewed from a direction perpendicular to the rotation axis A of the first and second shafts, and FIG. FIG. 4 is a perspective view showing a subassembly formed by a first guide collar and the like; 4 shows the positional relationship between the reduction gear and the tuning lever when viewed from the first shaft side parallel to the rotation axis A; FIG. 4 is a perspective view showing a portion of the gear case where a return spring is arranged on the first body side; 8A and 8B are schematic diagrams showing how the first and second valve bodies shift from the fully closed state to the default opening, and FIG. FIG. 10 is a schematic diagram schematically showing a state when shifting to an intermediate opening exceeding . 9A to 9D are schematic diagrams schematically showing how the first engagement portion of the return spring is assembled to the first contact portion of the first body. 10A to 10C are schematic diagrams schematically showing how the second engaging portion of the return spring is assembled to the second contact portion of the first body. FIG. 11 is a front view showing a first body side portion connected to a second body in an intake control device according to another embodiment of the present invention, viewed along direction D1 with the second body removed. 12 is a cross-sectional view taken along a plane parallel to directions D1 and D2 of FIG. 11; FIG.

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1A shows an intake control device according to one embodiment of the present invention. As shown in FIG. 1A, this intake control device 1 includes a first body 3 internally provided with a first intake passage 2 and a third intake passage 2a, and a second intake passage 4 and a fourth intake passage 4a therein. a second body 5, first and second shafts 6 and 7 rotatably supported by the first and second bodies 3 and 5, respectively, and a first valve body 8 arranged in the first intake passage 2 , a second valve body 9 arranged in the second intake passage 4, a third valve body 8a arranged in the third intake passage 2a, and a fourth valve body arranged in the fourth intake passage 4a. 9a.

The first and second valve bodies 8 and 9 are attached to the first and second shafts 6 and 7, respectively, and the rotation of the first and second shafts 6 and 7 causes the first and second intake passages 2 and 2 to open. Increase or decrease the passage cross-sectional area of 4. The first and second bodies 3 and 5 are fixed to each other so that the rotation axes of the first and second shafts 6 and 7 are arranged substantially on the same straight line (rotation axis A).

FIG. 1B shows the portion of the first body 3 side connected to the second body 5 with the second body 5 removed. FIG. 1B shows the first body 3 side portion of the gear case 10 housing a gear mechanism and the like for transmitting power to the first and second shafts 6 and 7 .

As shown in FIG. 1B, the first shaft 6 of the first body 3 is provided with a rotating lever 11 that is non-rotatably supported to impart a rotational force to the first shaft 6 . The intake control device 1 also includes first and second biasing members acting between the rotating lever 11 and the first body 3 to apply a rotational force to the rotating lever 11 about the rotation axis of the first shaft 6. Prepare.

Each of the first and second biasing members is a coil spring formed by winding a wire in a cylindrical shape. Either one of the first and second biasing members is a return spring that biases the rotating lever 11 in the direction in which the first valve body 8 reduces the passage cross-sectional area of the first intake passage 2, and the other is: It is a default spring that biases the rotating lever 11 in the direction in which the first valve body 8 increases the passage cross-sectional area of the first intake passage 2 . In this embodiment, the first biasing member is the return spring 12 and the second biasing member is the default spring 13 .

The return spring 12 is arranged closer to the first valve body 8 than the rotating lever 11 in the D1 direction parallel to the rotation axis A of the first and second shafts 6 and 7 . The default spring 13 is arranged farther from the first valve body 8 than the rotating lever 11 in the D1 direction. Both the return spring 12 and the default spring 13 are arranged so that the center line of their cylindrical shape overlaps the rotation axis A of the first and second shafts 6 and 7 .

The rotating lever 11 is a lever gear driven by a reduction gear 14 and has a gear portion 15 . The reduction gear 14 is rotatably supported by the first body 3 about a rotation axis parallel to the rotation axis A of the first and second shafts 6 and 7, and is rotatable on the parallel rotation axis. It is composed of a large-diameter gear 16 and a small-diameter gear 17 which are arranged in an impossibility. The small-diameter gear 17 is arranged closer to the first body 3 than the large-diameter gear 16 and meshes with the gear portion 15 of the rotating lever 11 .

The large-diameter gear 16 meshes with a pinion gear 19 provided on the rotating shaft of the motor 18 . Therefore, the rotation lever 11 is rotated by the motor 18 via the pinion gear 19 and the reduction gear 14, and the opening degrees of the first and second valve bodies 8 and 9 are adjusted.

FIG. 2 shows the inside of the first and second bodies 3 and 5 at the connecting portion of the first and second bodies 3 and 5, along with the rotation axis A of the first and second shafts 6 and 7 and the rotation axis of the reduction gear 14. , along the D2 direction (see FIG. 1B) parallel to the first reference line 20, which is orthogonal to both. As shown in FIG. 2, when viewed in the D2 direction, the return spring 12 extends at least partially from the outer peripheral surface of a substantially cylindrical first shaft support portion 21 that is provided in the first body 3 and supports the first shaft 6. are arranged so that they overlap.

When viewed in the D2 direction, the default spring 13 is arranged so that at least a portion of the outer peripheral surface of the substantially cylindrical second shaft support portion 22 that is provided in the second body 5 and supports the second shaft 7 overlaps. be done.

FIG. 3 shows the connecting portion of the first and second bodies 3, 5 with the first and second bodies 3, 5 removed. As shown in FIG. 3, a tuning lever 23 held by the second shaft 7 so as not to be mutually rotatable with the second shaft 7 is arranged on the second shaft 7 closer to the first shaft 6 than the second valve body 9 is. be. The movements of the first shaft 6 and the second shaft 7 about the rotation axis A are synchronized by a connecting mechanism 24 connecting the rotating lever 11 and the tuning lever 23 .

The return spring 12 includes a first locking portion 25 extending radially outward from the center of the cylindrical shape of the first shaft supporting portion 21 (see FIG. 2) and locked to the first body 3, and A second engaging portion 26 extending outward and capable of contacting both the rotating lever 11 and the first body 3 is provided.

The default spring 13 includes a third locking portion 27 extending radially outward from the center of the cylindrical shape of the second shaft supporting portion 22 (see FIG. 2) and locked to the second body 5, and A fourth locking portion 28 extending outwardly and capable of coming into contact with both the tuning lever 23 and the second body 5 is provided.

FIG. 4A shows the configuration of the first body 3 side related to the rotating lever 11 . As shown in FIG. 4A , the first body 3 has a first contact portion 25 a that contacts the first locking portion 25 of the return spring 12 and a second contact portion 29 that contacts the second locking portion 26 . Prepare. The second contact portion 29 causes the return spring 12 to apply torque in the closing direction to the rotating lever 11 when the opening degrees of the first and second valve bodies 8 and 9 are equal to or less than a default angle α, which will be described later. to prevent The rotating lever 11 includes a first fully closed arm portion 30 and a first spring arm portion 31 extending in the radial direction.

The first fully-closed arm portion 30 has a function of contacting a first fully-closed adjustment screw 33 protruding from the case inner wall surface 32 of the gear case 10 to determine the fully-closed position of the rotating lever 11 . This fully closed position is the position of the rotating lever 11 when the first and second valve bodies 8 and 9 are in the fully closed state. The first spring arm portion 31 has a function of contacting the second locking portion 26 of the return spring 12 and transmitting the urging force of the return spring 12 in the closing direction to the rotating lever 11 .

Further, the rotating lever 11 includes a first connecting arm portion 34 as a component on the rotating lever 11 side of a connecting mechanism 24 (see FIG. 3) that connects the rotating lever 11 and the tuning lever 23 . The first connecting arm portion 34 includes a spring boss 35 erected on the side of the tuning lever 23 (see FIG. 3) in the D1 direction, a screw boss 36 erected so as to face the spring boss 35, and a screw boss 36 and a spring guide shaft 40 supported by a spring boss 35 via a restraining spring 39 so that the tip face of the tuning screw 38 faces the tip face of the tuning screw 38. Prepare. A first guide collar 41 that guides the return spring 12 is provided between the rotating lever 11 and the first shaft support portion 21 (see FIG. 2).

When assembling the rotating lever 11, the first shaft 6, the first guide collar 41, etc. to the first body 3, these can be assembled as a sub-assembly.

This subassembly includes a shaft assembly including the first shaft 6 and the pivot lever 11, which is inserted inside the first guide collar 41 so that the first guide collar 41 is inserted into the pivot lever 11. In addition, an O-ring 6a is fitted in a groove provided on the outer periphery of the first shaft 6 so that the outer diameter of the O-ring 6a is larger than the inner diameter of the first guide collar 41. and is configured to hold the first guide collar 41 with the O-ring 6a.

By arranging the return spring 12 on the opposite side of the rotary lever 11 of the first guide collar 41 in this small assembly and inserting the first shaft 6 into a predetermined position of the first body 3, the small assembly is moved to the first position. It can be attached to the body 3.

Since the first guide collar 41 is held by the O-ring 6a in the subassembly so as not to separate from the pivot lever 11, this assembly can be performed without holding down the first guide collar 41. As shown in FIG. After assembly, the O-ring 6a functions to keep the first shaft 6 and the first body 3 airtight. Similarly, the second shaft 7, the tuning lever 23, the second guide collar 50, etc. on the second body 5 side can also be assembled to the second body 5 as a small assembly as shown in FIG. 5B.

FIG. 4B shows the configuration of the second body 5 related to the tuning lever 23 . As shown in FIG. 4B , the second body 5 includes a third contact portion 42 that contacts the third locking portion 27 of the default spring 13 and a fourth contact portion 43 that contacts the fourth locking portion 28 . , a second full-close adjustment screw 44 that defines the full-close position of the tuning lever 23, and a fourth slope 45 that is adjacent to the fourth contact portion 43 and has a function to be described later.

The fourth contact portion 43 is configured so that the default spring 13 applies torque in the opening direction to the tuning lever 23 when the opening degrees of the first and second valve bodies 8 and 9 are equal to or greater than a default angle α, which will be described later. prevent When viewed in the D1 direction (extending direction of the second shaft 7), the fourth contact portion 43 is arranged within the movable rotation range of the rotating lever 11 (see FIG. 8C), as will be described later.

The tuning lever 23 is brought into the fully closed position by coming into contact with the second spring arm portion 46 which receives the urging force in the opening direction from the default spring 13 via the fourth engaging portion 28 and the second full-close adjustment screw 44 . and a second fully closed arm 47 on which the tuning lever 23 is positioned.

The tuning lever 23 also includes a second connecting arm portion 48 that constitutes the tuning lever 23 side of the connecting mechanism 24 . The second connecting arm portion 48 includes a clamped plate portion 49 clamped between the tuning screw 38 of the first connecting arm portion 34 and the spring guide shaft 40 . A second guide collar 50 made of resin is provided between the tuning lever 23 and the default spring 13 to guide the default spring 13 so that it operates smoothly.

FIG. 5A shows the positional relationship between the reduction gear 14 and the tuning lever 23 when viewed from a direction perpendicular to direction D1. As shown in FIG. 5A, the reduction gear 14 and the tuning lever 23 overlap when viewed from a direction perpendicular to the D1 direction. Therefore, the movable range of the tuning lever 23 is limited by the reduction gear 14 .

FIG. 6 shows the positional relationship between the reduction gear 14 and the tuning lever 23 when viewed in the D1 direction. Since the movable range of the tuning lever 23 is limited by the reduction gear 14 as described above, it is necessary to set the rotation range of the tuning lever 23 so as not to contact the reduction gear 14, as shown in FIG. There is

That is, when the turning lever 11 does not receive a rotational force from the speed reduction gear 14, the default spring 13 causes the tuning lever 23 to move its fourth engaging portion 28 into contact with the fourth contacting portion 43, i.e., to the default position. It is positioned at a position rotated by a default angle α from the fully closed position. Note that the fully closed position is set so that the tuning lever 23 does not interfere with the reduction gear 14 .

In addition, the tuning lever 23 receives a rotational force from the reduction gear 14 via the rotating lever 11, so that the range from the default position to the fully closed position (the range of the default angle α) and the deceleration in the opening direction from the default position. It is rotated within the range of the movable angle β which is a position where it does not interfere with the gear 14 .

Therefore, the movable rotation range (α+β) of the tuning lever 23 including the default angle α and the movable angle β is set so that the tuning lever 23 does not interfere with the reduction gear 14 . In this embodiment, as shown in FIG. 6, the movable rotation range (α+β) is set to approximately 90°.

FIG. 7 shows a portion of the gear case 10 on the side of the first body 3 where the return spring 12 is arranged. As shown in FIG. 7, the first body 3 abuts against the opening direction side of the first fully closed arm portion 30 (see FIG. 4A) of the rotating lever 11 to fully open the first and second valve bodies 8 and 9. It has a fully open stopper boss 51 that defines the position. Further, the first body 3 is configured such that when at least one of the first and second contact portions 25 a and 29 is rotated around the rotation axis A of the first and second shafts 6 and 7 , A slope is provided within the range of the trajectory and gradually increases in height from the first body 3 toward the rotating lever 11 side.

Specifically, as the slope, the first slope 52 is arranged within the range of the trajectory when the first contact portion 25a is rotated around the rotation axis A when viewed in the D1 direction. The first slope 52 increases in height as the first locking portion 25 of the return spring 12 advances in the direction of rotation of the first body 3 through the first contact portion 25a to apply a rotational force to the first body 3. , and reaches the upper end surface of the fully open stopper boss 51 .

Further, as the slope, the second slope 53 is arranged within the range of the trajectory when the second contact portion 29 is rotated around the rotation axis A when viewed in the D1 direction. The second slope 53 increases in height as the second locking portion 26 of the return spring 12 advances in the direction opposite to the rotational direction in which the rotational force is applied to the first body 3 via the second contact portion 29 . It gradually increases to the height of the contact portion 29 and reaches the upper end surface of the second contact portion 29 .

As a similar slope, the second body 5 is provided with a fourth slope 45 shown in FIG. 4B. The fourth slope 45 gradually increases in height from the second body 5 toward the tuning lever 23 side around the rotation axis A of the fourth contact portion 43 . That is, the fourth slope 45 is arranged within a locus range when the fourth contact portion 43 is rotated around the rotation axis A when viewed in the D1 direction, and the fourth locking portion 28 of the default spring 13 is located at the fourth slope. The height gradually increases to the height of the fourth contact portion 43 in the direction opposite to the rotational direction in which the rotational force is applied to the second body 5 via the contact portion 43 , and the upper end surface of the fourth contact portion 43 . has reached

In this configuration, the rotating lever 11 and the tuning lever 23 are connected by the connecting mechanism 24, so they rotate together. At this time, when the opening degrees of the first and second valve bodies 8 and 9 are smaller than the default angle α, the default spring 13 causes the rotation lever 11 and the tuning lever 23 to move through the fourth locking portion 28 thereof. is applied with a biasing force (torque) in the opening direction.

When the opening degrees of the first and second valve bodies 8 and 9 are larger than the default angle α, the return spring 12 exerts an urging force on the rotating lever 11 and the tuning lever 23 through the second locking portion 26 in the closing direction. (torque) is applied. When the opening degrees of the first and second valve bodies 8 and 9 are the default angle α, the fourth locking portion 28 and the second locking portion 26 are respectively the fourth contact portion 43 and the second contact portion 43 . Since it is in contact with the portion 29, no torque is applied to the rotating lever 11 and the tuning lever 23.

Therefore, when the torque applied to the rotating lever 11 by the default spring 13 and the return spring 12 and the torque applied to the rotating lever 11 by the motor 18 via the reduction gear 14 are balanced, the rotating lever 11 and the tuning lever 11 are balanced. The opening degrees of the first and second valve bodies 8 and 9 are determined by the position of the lever 23 .

8A and 8B schematically show how the first and second valve bodies 8 and 9 shift from the fully closed state to the default opening state. FIG. 8A shows the positions of the rotating lever 11 and the tuning lever 23, the default spring 13 and the like when the first and second valve bodies 8 and 9 are in the fully closed state. This fully closed state is maintained against the urging force of the default spring 13 in the opening direction until the rotating lever 11 and the tuning lever 23 are brought into contact with the first and second fully closing adjusting screws 33 and 44 by the motor 18, respectively. It is generated by rotating in the arrow Y1 direction.

In this fully closed state, if the motor 18 stops for some reason, the torque applied by the default spring 13 via the fourth locking portion 28 causes the tuning lever 23 and the rotating lever 11 to move in the opening direction (arrow Y2 direction). ). This rotation stops when the fourth locking portion 28 of the default spring 13 contacts the fourth contact portion 43 and the opening reaches the default angle α, as shown in FIG. 8B. At this time, the second locking portion 26 of the return spring 12 is in contact with the second contact portion 29, and the torque is not applied to the rotating lever 11, so the default angle α is maintained. That is, the first and second valve bodies 8 and 9 are brought into the default opening state shown in FIG. 8B and maintained in that state.

In the state of the default opening, the opening of the first and second valve bodies 8 and 9 is maintained at the default angle α. Reserved by the device 1 . This ensures the minimum engine drive required for the vehicle to evacuate on public roads.

FIG. 8C schematically shows a state in which the first and second valve bodies 8 and 9 are in an intermediate opening state exceeding the default opening. At the intermediate opening, as shown in FIG. 8C, the second locking portion 26 of the return spring 12 is pushed by the first spring arm portion 31 of the rotating lever 11 and separated from the second contact portion 29. A biasing force in the closing direction is applied to the rotating lever 11 by the return spring 12 . A desired intermediate opening degree is achieved by rotating the rotating lever 11 in the opening direction (arrow Y2 direction) by the torque from the motor 18 against this biasing force.

In this state, if the motor 18 stops for some reason, the urging force of the return spring 12 in the closing direction rotates the tuning lever 23 and the rotating lever 11 in the closing direction (arrow Y1 direction). 8B, the second locking portion 26 of the return spring 12 contacts the second contact portion 29, and the second spring arm portion 46 of the tuning lever 23 contacts the fourth contact portion of the default spring 13, as shown in FIG. 8B. It is performed until it abuts on the engaging portion 28 .

With this abutment achieved, the first and second valve bodies 8, 9 are positioned at the default angle α. In this state, no torque is applied from the return spring 12 and the default spring 13 to the rotating lever 11 and the tuning lever 23 . As a result, the first and second valve bodies 8 and 9 are brought into the default opening state shown in FIG. 8B, and this state is maintained.

9A to 9D schematically show how the first engaging portion 25 of the return spring 12 is assembled to the first contact portion 25a of the first body 3. FIG. In this assembly, if the direction of rotation indicated by an arrow R in the drawing (the clockwise direction when viewed from above) is the R direction, the return spring 12 is first rotated by its second locking portion 26. It is arranged on the rotating lever 11 so as to be positioned on the R direction side of the first spring arm portion 31 of the lever 11 . Then, the return spring 12 is assembled so that the first engaging portion 25 of the return spring 12 is engaged with the first contact portion 25a of the first body 3. It is not necessary to be positioned precisely between the portion 25a and the fully open stopper boss 51, and the first locking portion 25 of the return spring 12 is positioned on the front side of the first slope 52 in the R direction as shown in FIG. The rotating lever 11 and the return spring 12 may be positioned on the first body 3 so as to do so. Hereinafter, a case where the first locking portion 25 is positioned on the front side of the first slope 52 will be described.

Next, the rotating lever 11 is rotated along the R direction to twist the return spring 12 . After that, when the first locking portion 25 of the return spring 12 reaches the first slope 52, the first locking portion 25 climbs the first slope 52 as shown in FIG. Get over the fully open stopper boss 51. Further, when the rotating lever 11 is rotated, the first engaging portion 25 comes into contact with the first contact portion 25a as shown in FIG. 9D. As a result, the first engaging portion 25 of the return spring 12 can be assembled to the first contact portion 25 a without being accidentally assembled to the full-open stopper boss 51 .

10A to 10C schematically show how the second locking portion 26 of the return spring 12 is assembled to the second contact portion 29 of the first body 3. FIG. That is, first, as shown in FIG. 10A, the first locking portion 25 of the return spring 12 is assembled to the first contact portion 25a, and the second locking portion 26 of the return spring 12 is attached to the second slope 53 in the R direction. The return spring 12 and the rotating lever 11 are positioned on the first body 3 in a state where the first spring arm portion 31 of the rotating lever 11 is positioned on the front side and in front of the second locking portion 26 .

Next, the rotating lever 11 is rotated along the R direction to twist the return spring 12 . After that, when the second locking portion 26 of the return spring 12 reaches the second slope 53, as shown in FIG. 10B, the second locking portion 26 climbs the second slope 53, and as shown in FIG. It climbs over the second contact portion 29 and comes into contact with the R-direction side of the second contact portion 29 .

As a result, it is not necessary for the operator to once move the rotating lever 11 away from the first body 3 to move the second locking portion 26 over the second contact portion 29, and the second locking portion 26 is moved to the second contact portion 29. 2 contact portion 29 can be assembled. Therefore, the second locking portion 26 can be secured while preventing the first locking portion 25 from being disengaged from the first contact portion 25a due to the pivotal lever 11 moving away from the first body 3 unintentionally. It can be assembled to the second contact portion 29 .

The operation of assembling the fourth locking portion 28 of the default spring 13 to the fourth contact portion 43 of the second body 5 can also be performed in the same manner as in FIGS. 10A to 10C. That is, the default spring 13 is the return spring 12, the fourth locking portion 28 is the second locking portion 26, the third locking portion 27 is the first locking portion 25, the fourth slope 45 is the second slope 53, and the second By associating the spring arm portion 46 with the first spring arm portion 31 and the tuning lever 23 with the rotating lever 11, they can be assembled in the same manner.

As described above, according to the present embodiment, the return spring 12 is arranged closer to the first valve body 8 than the rotating lever 11 in the D1 direction, and the default spring 13 is closer to the first valve body than the rotating lever 11. 8, and the return spring 12 and the default spring 13 are arranged so that the center line of the cylindrical shape overlaps with the rotation axis A, so that the degree of freedom of arrangement is improved and the intake control in the D1 direction is improved. Miniaturization of the device 1 can be easily achieved.

Further, when viewed in the second direction, the return spring 12 is arranged so as to overlap the outer peripheral surface of the substantially cylindrical first shaft support portion 21 that supports the first shaft 6 , and the default spring 13 is arranged so as to overlap the second shaft 7 . , so that when the default mechanism is arranged between the first and second bodies 3 and 5, the return spring can be made compact in the D1 direction. 12 and default spring 13 can be arranged.

Further, the first body 3 is provided with a second contact portion that contacts the second locking portion 26 of the return spring 12 , and the second body 5 is provided with a fourth contact portion that contacts the fourth locking portion 28 of the default spring 13 . Since the portion 43 is provided, the fourth contact portion 43 can be arranged within the movable rotation range of the rotating lever 11 when viewed in the D1 direction. As a result, the intake control device 1 can be configured more compactly in the D1 direction.

In addition, since a portion of the default spring 13 overlaps the large-diameter gear 16 when viewed in the D2 direction, the intake control device 1 can be configured more compactly in the D1 direction.

Further, since the first slope 52 is arranged adjacent to the fully open stopper boss 51 within the range of the trajectory when the first contact portion 25a is rotated around the rotation axis A, the return spring 12 is first locked. The portion 25 can be assembled to the first contact portion 25 a without erroneously assembling to the full-open stopper boss 51 .

Further, since the second slope 53 is arranged adjacent to the second contact portion 29 within the range of the trajectory when the second contact portion 29 is rotated around the rotation axis A, when the return spring 12 is assembled, It is not necessary for the operator to once move the rotating lever 11 away from the first body 3 to move the second locking portion 26 over the second contact portion 29, and the second locking portion 26 can be easily moved. It can be brought into contact with the second contact portion 29 .

In addition, since the fourth slope 45 adjacent to the fourth contact portion 43 is provided, the fourth locking portion 28 of the default spring 13 is easily brought into contact with the fourth contact portion 43, and the default spring 13 is assembled. be able to.

FIG. 11 shows a portion of an intake control device 1b according to another embodiment of the present invention on the side of a first body 3b connected to a second body 5b, viewed in the direction D1 with the second body 5b removed. show. FIG. 12 shows a state in which FIG. 11 is cut along a plane parallel to the directions D1 and D2. FIG. 11 shows a portion of the gear case 10b on the side of the first body 3b. The intake control device 1b of this embodiment differs from the intake control device 1 of FIG. 1A in the default mechanism for positioning the first and second valve bodies 8 and 9 at the default angles.

The configuration and operation of the intake control device 1b other than those mentioned here are the same as those of the intake control device 1 of FIG. 1A. In the intake control device 1b, the movable rotation range, which is the range in which the first shaft 6b can be rotated, is set to 90 degrees or less.

As shown in FIGS. 11 and 12, in this embodiment, the cylindrical outer diameter r1 of the default spring 13b is equal to the diameter r2 of the reference pitch circle of the gear portion 15b of the rotating lever 11b and the reference pitch of the small diameter gear 17b. It is smaller than the difference between the sum of the diameter r3 of the circle and the diameter r4 of the addendum circle of the large gear 16b (r1<r2+r3-r4).

The default spring 13b is guided and held by a guide nut 54 screwed onto the end of the first shaft 6b. At least part of the default spring 13b is arranged so as to overlap the large-diameter gear 16b when viewed in the D2 direction.

The default spring 13b has a third locking portion 27b extending radially outward from the center of the cylindrical shape and locked to the first connecting arm portion 34b of the rotating lever 11b, and a third locking portion 27b extending radially outward. and a fourth locking portion 28b capable of coming into contact with both the first spring arm portion 31b of the rotating lever 11b and the fourth contact portion 43b of the first body 3b.

The default spring 13b applies torque to the rotating lever 11b by contacting both the third and fourth engaging portions 27b and 28b to the rotating lever 11b when the rotating lever 11b is positioned at the default position described later. It will not be granted. As shown in FIG. 12, the fourth locking portion 28b is arranged so as to overlap the large-diameter gear 16b when viewed in the direction D2.

The position of the rotating lever 11b with respect to the first body 3b when only the biasing force from the return spring 12b and the default spring 13b can act on the rotating lever 11b (when the torque from the motor 18 is not applied to the rotating lever 11b). is the default position. Then, the rotation angle about the rotation axis A of the first shaft 6b when the rotating lever 11b is rotated from the default position to the fully closed position where the first spring arm portion 31b contacts the fully closed adjusting screw 33b is Assuming a default angle γ, the default angle γ is 45 degrees or less.

When viewed in the D1 direction parallel to the rotation axis A of the first shaft 6b, a first line segment 55 connecting the rotation axis A to the large-diameter gear 16b side of the third locking portion 27b is formed with the rotation axis A as the center. The large-diameter gear 16b is arranged outside the fan-shaped range expressed as a trajectory rotated by the default angle γ toward the large-diameter gear 16b. This avoids interference between the third locking portion 27b and the large-diameter gear 16b.

According to the intake control device 1b of the present embodiment, the return spring 12b is arranged so as to overlap with the outer peripheral surface of the first shaft support portion 21b of the first body 3b, and the default spring 13b is viewed in the direction of D2 to form a large-diameter gear. 16b, the default angle .gamma. It can be configured compactly.

Although the embodiment of the present invention has been described above, the present invention is not limited to this. For example, in the above description, the fourth contact portion 43 is arranged within the movable rotation range of the rotating lever 11 when viewed from the D1 direction. Both the contact portion 29 and the fourth contact portion 43 may be arranged within the movable rotation range of any one of the rotating lever 11 , the tuning lever 23 and the connecting mechanism 24 .

1, 1b... Intake control device 2... First intake passage 2a... Third intake passage 3, 3b... First body 4... Second intake passage 4a... Fourth intake passage 5, 5b... Second intake passage Body 6, 6b First shaft 6a O-ring 7 Second shaft 8 First valve body 8a Third valve body 9 Second valve body 9a Fourth valve body 10 , 10b... Gear case 11, 11b... Rotating lever 12, 12b... Return spring 13, 13b... Default spring 14... Reduction gear 15, 15b... Gear portion 16, 16b... Large diameter gear 17, 17b...small diameter gear 18...motor 19...pinion gear 20...first reference line 21, 21b...first shaft support portion 22...second shaft support portion 23...tuning lever 24...connection mechanism 25 1st locking portion 25a 1st contacting portion 26 2nd locking portion 27, 27b 3rd locking portion 28, 28b 4th locking portion 29 2nd contacting portion , 30... First fully closed arm 31, 31b... First spring arm 32... Case inner wall surface 33... First fully closed adjusting screw 33b... Fully closed adjusting screw 34, 34b... First connecting arm Part 35... Spring boss 36... Screw boss 37... Anti-loosening spring 38... Tuning screw 39... Holding spring 40... Spring guide shaft 41... First guide collar 42... Third contact part 43 , 43b... Fourth contact portion, 44... Second fully closed adjusting screw, 45... Fourth slope, 46... Second spring arm, 47... Second fully closed arm, 48... Second connecting arm, 49 Plate portion to be clamped 50 Second guide collar 51 Fully open stopper boss 52 First slope 53 Second slope 54 Guide nut 55 First line segment A Rotation axis α γ: default angle.

Claims (2)

a first body having a first intake passage therein;
a first shaft rotatably supported by the first body;
a first valve body disposed in the first intake passage and attached to the first shaft for increasing or decreasing the passage cross-sectional area of the first intake passage as the first shaft rotates;
a rotating lever supported by the first shaft so as not to be mutually rotatable and imparting a rotational force to the first shaft;
a first biasing member and a second biasing member acting between the rotating lever and the first body to apply a rotational force to the rotating lever about the rotation axis of the first shaft;
Both the first biasing member and the second biasing member are coil springs formed by winding wire in a cylindrical shape,
One of the first biasing member and the second biasing member is a return spring that biases the rotating lever in a direction in which the first valve body reduces the cross-sectional area of the passage, and the other is the rotating lever. In the intake control device, wherein the first valve body is a default spring that biases the movement lever in the direction of increasing the cross-sectional area of the passage,
The first biasing member is arranged closer to the first valve body than the rotating lever in a first direction parallel to the rotation axis of the first shaft,
The second biasing member is arranged on the side opposite to the first valve body with respect to the rotating lever in the first direction,
Both the first biasing member and the second biasing member are arranged so that the center line of the cylindrical shape thereof overlaps the rotation axis of the first shaft,
The intake control device further comprises:
a second body having a second intake passage therein;
a second shaft rotatably supported by the second body;
a second valve body disposed in the second intake passage and attached to the second shaft for increasing or decreasing the passage cross-sectional area of the second intake passage as the second shaft rotates;
a reduction gear that is rotatably supported by the first body about a rotational axis parallel to the first direction and that transmits rotational force to the rotating lever;
The first body and the second body are fixed to each other such that the rotation axis of the first shaft and the rotation axis of the second shaft are arranged substantially on the same straight line,
When viewed from a direction parallel to a first reference line orthogonal to both the rotation axis of the first shaft and the rotation axis of the reduction gear, the first biasing member is provided in the first body and is arranged in the first direction. arranged so as to at least partially overlap the outer peripheral surface of the substantially cylindrical first shaft support portion that supports the shaft,
When viewed in a direction parallel to the first reference line, the second biasing member is provided on the second body to support the second shaft. are arranged so that the parts overlap,
The intake control device further comprises:
a tuning lever disposed closer to the first shaft than the second valve body of the second shaft and held by the second shaft so as not to be mutually rotatable with the second shaft;
a connecting mechanism that connects the rotating lever and the tuning lever to synchronize the movements of the first shaft and the second shaft about their rotation axes;
The first biasing member includes a first locking portion extending radially outward from the center line of the cylindrical shape of the first shaft support portion and locked to the first body; a second locking portion that extends and is capable of coming into contact with both the rotating lever and the first body;
The second biasing member includes a third locking portion extending radially outward from the center line of the cylindrical shape of the second shaft support portion and locked to the second body; a fourth locking portion that extends and is capable of coming into contact with both the tuning lever and the second body;
The first body includes a second contact portion that contacts the second locking portion,
The second body includes a fourth contact portion that contacts the fourth locking portion,
When viewed in the first direction, at least one of the second contact portion and the fourth contact portion is within a movable rotation range of any one of the rotating lever, the tuning lever, and the connecting mechanism. An intake control device, characterized in that it is arranged . a first body having a first intake passage therein;
a first shaft rotatably supported by the first body;
a first valve body disposed in the first intake passage and attached to the first shaft for increasing or decreasing the passage cross-sectional area of the first intake passage as the first shaft rotates;
a rotating lever supported by the first shaft so as not to be mutually rotatable and imparting a rotational force to the first shaft;
a first biasing member and a second biasing member acting between the rotating lever and the first body to apply a rotational force to the rotating lever about the rotation axis of the first shaft;
Both the first biasing member and the second biasing member are coil springs formed by winding wire in a cylindrical shape,
The first biasing member is a return spring that biases the rotating lever in the direction in which the first valve body reduces the passage cross-sectional area, and the second biasing member moves the rotating lever to the first position. In an intake control device in which the valve body is a default spring that biases in the direction of increasing the passage cross-sectional area,
The first biasing member is arranged closer to the first valve body than the rotating lever in a first direction parallel to the rotation axis of the first shaft,
The second biasing member is arranged on the side opposite to the first valve body with respect to the rotating lever in the first direction,
Both the first biasing member and the second biasing member are arranged so that the center line of the cylindrical shape thereof overlaps the rotation axis of the first shaft,
a movable rotation range of the first shaft is set to 90 degrees or less,
the rotating lever is a lever gear driven by a reduction gear;
The reduction gear includes a large-diameter gear supported by the first body so as to be rotatable about a rotation axis parallel to the first direction, and non-rotatably arranged on the parallel rotation axis; Consists of small diameter gears,
The small-diameter gear is arranged closer to the first body than the large-diameter gear and meshes with the lever gear,
When viewed in a second direction parallel to a first reference line perpendicular to both the rotation axis of the first shaft and the rotation axis of the reduction gear, the first biasing member is provided on the first body and arranged so as to at least partially overlap the outer peripheral surface of a substantially cylindrical first shaft support portion that supports the first shaft;
The outer diameter of the cylindrical shape of the second biasing member is the difference between the sum of the diameter of the reference pitch circle of the lever gear and the diameter of the reference pitch circle of the small-diameter gear, and the diameter of the addendum circle of the large-diameter gear. smaller,
at least part of the second biasing member is arranged to overlap the large-diameter gear when viewed in the second direction;
The second biasing member includes a third engaging portion extending radially outward from the center of the cylindrical shape and engaged with the rotating lever, and a third engaging portion extending radially outwardly and engaging the rotating lever. a fourth locking portion capable of coming into contact with both the lever and the first body;
The fourth locking portion is arranged so as to overlap with the large-diameter gear when viewed in the second direction,
a positional relationship between the rotating lever and the first body when only biasing forces from the first biasing member and the second biasing member can act on the rotating lever; to the fully closed position where the first valve body is fully closed, the default angle is 45. degrees or less,
When viewed in the first direction, a first line segment connecting the rotation axis of the first shaft to the large-diameter gear side of the third locking portion is formed around the rotation axis of the first shaft. An intake control device, wherein the large-diameter gear is arranged outside a fan-shaped range expressed as a trajectory rotated by the default angle on the gear side.

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