KR20180108995A - Appratus controlling intake air for engine of vehicle - Google Patents

Abstract

The present invention relates to an apparatus to control intake air of a vehicle, capable of effectively operating a plurality of valves. According to the present invention, the apparatus to control intake air of a vehicle comprises: an intake flow path, wherein a flowing pipe to supply the intake air is divided to form a plurality of divided flow paths, and the divided flow paths simultaneously communicate with the same combustion chamber; an intake valve disposed in the flowing pipe and adjusting the opening degree of the flowing pipe in accordance with a rotational angle; a swirl valve disposed in any one of the divided flow paths and adjusting the opening degree of the divided flow path in accordance with an rotational angle; and a cam plate coupled to the swirl valve to be rotated and having a cam hole formed thereon. The intake valve has an insertion protrusion inserted into the cam hole at a position separated from a rotary shaft thereof and at least a part of section of the cam hole is rotated on the central axis of the intake valve while the insertion protrusion is slid in accordance with rotation of the swirl valve, and thus a first rotational section to rotate the intake valve is formed.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to an intake control device for a vehicle, and more particularly, to an intake control device for controlling an intake flow into an engine.

A plurality of combustion chambers may be provided in the engine, and a flow path for the intake air to flow into each combustion chamber may be provided. The flow path may be provided with a valve for regulating the flow amount of the intake air by adjusting the flow cross sectional area of the intake air.

Meanwhile, the amount of intake air flowing into each combustion chamber of the engine can be adjusted according to the running condition of the vehicle, and the intake amount can be controlled by using the valve. It is an important task for the vehicle to appropriately control the flow of the intake air flowing into the combustion chamber depending on the driving situation.

It should be understood that the foregoing description of the background art is merely for the purpose of promoting an understanding of the background of the present invention and is not to be construed as an admission that the prior art is known to those skilled in the art.

KR 20-1996-0008470 A1

An object of the present invention is to provide an intake control device capable of effectively operating a plurality of valves that simultaneously control the intake flow while simplifying the structure.

In order to achieve the above object, an intake control device for a vehicle according to the present invention includes: an intake air flow passage formed to divide a flow pipe through which an intake air flows, thereby forming a plurality of divided flow paths; An intake valve provided in the flow pipe, the intake valve being provided to adjust the opening degree of the flow pipe according to the rotation angle; A swirl valve provided on any one of the plurality of divided flow paths and adapted to adjust the opening of the divided flow path according to the rotation angle; And a cam plate rotatably coupled to the swirl valve and having a cam groove formed therein, wherein the intake valve is provided with an insertion protrusion which is inserted into the cam groove at a position spaced apart from the rotation axis thereof, and at least a part of the cam groove is engaged with the rotation of the swirl valve The insertion protrusion is slid along the center axis of the intake valve, thereby forming a first rotation section for rotating the intake valve.

The plurality of divided flow paths are respectively branched to form a plurality of branched flow paths, and a plurality of branch flow paths are provided so as to communicate with the plurality of combustion chambers formed in the engine, respectively.

The first rotation section of the cam groove is provided such that the distance from the rotation axis of the swirl valve is changed along the longitudinal direction so that the insertion projection is rotated while sliding on the first rotation section.

The first rotation section may be formed in a curved shape such that the rotation angle of the intake valve due to the sliding insertion protrusions is uniform with respect to the rotation angle of the swirl valve.

The cam groove may be formed with a non-rotating section having a constant distance from the rotation axis of the swirl valve along the longitudinal direction so that the insertion protrusion slidable in at least a part of the section except for the first rotation section is not rotated.

When the swirl valve is rotated in one direction from the reference state corresponding to the maximum open state of the intake valve, the cam groove of the cam plate is provided so that the insertion projection is located on the first rotation section, A swirl groove is formed in the swirl valve so that the swirl valve can be further rotated in one direction from the set angle.

When the swirl valve is rotated from the reference state to the other direction, the cam groove of the cam plate is provided such that the insertion projection is positioned on the non-rotating section.

The first rotation section may be formed in a curved shape so that the rotation angle of the intake valve due to the sliding insertion protrusion has a constant ratio with respect to the rotation angle of the swirl valve.

A driving unit for providing rotational force to the swirl valve; And a control unit for controlling the rotation angle of the swirl valve so as to slide the insertion projection in the first rotation period in a regeneration mode of the DPF apparatus provided on the exhaust flow path, And the opening degree of the swirl valve is adjusted within the rotation groove section.

The cam groove has a second rotation section in which at least a section of the cam groove except for the non-rotation section is rotated while the insertion projection is slid according to the rotation of the swirl valve, and a non-rotation section is formed between the first rotation section and the second rotation section And a section is provided.

When the swirl valve is rotated from the reference state corresponding to the maximum open state of the intake valve to the other direction, the cam groove of the cam plate is provided such that the insertion projection is positioned on the non-rotating section or the second rotating section .

A driving unit for providing rotational force to the swirl valve; The control unit adjusts the rotation angle of the swirl valve so that the insertion protrusion slides in the second rotation interval in the regeneration mode of the LNT apparatus provided on the exhaust passage, and the controller controls the rotation angle of the swirl valve by controlling the driving unit. The rotation angle of the swirl valve is adjusted so that the insertion projection slides in the first rotation section in the regeneration mode of the DPF device provided on the exhaust passage, and the opening degree of the swirl valve is adjusted within the rotation groove section .

According to the intake control device of the vehicle constructed as described above, it is possible to effectively operate a plurality of valves that regulate the intake flow while simplifying the structure.

Further, by driving the intake valve through the swirl valve, the degree of freedom of operation of the valve can be improved, for example, by adjusting the rotational angle ratio between the driving portion and the valve or keeping the valve in the non-rotating state despite the driving portion.

In addition, the cam plate can be transmitted to the intake valve by the rotational force transmitted to the swirl valve according to the shape of the cam groove, so that the plurality of valves can be operated as a single driving unit, thereby simplifying the structure and reducing weight.

In addition, the plurality of valves can be adjusted by a single driving unit according to the running state of the vehicle through the control unit, so that the intake flow according to the running state can be effectively satisfied.

Further, it is not necessary to simplify the cam groove shape and to apply the insertion projection structure to the swirl valve, so that the swirl valve can be simply manufactured in a simple structure.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a view showing an intake and exhaust system equipped with an intake control device for a vehicle according to an embodiment of the present invention;
FIG. 2 is a view showing an intake passage on which an intake control device for a vehicle is mounted according to an embodiment of the present invention;
3 is a view showing a reference state of an intake air control apparatus for a vehicle according to a first embodiment of the present invention,
4 is a view illustrating a state in which the swirl valve is rotated in one direction in the intake air control apparatus of the vehicle according to the first embodiment of the present invention so that the opening degree of the intake valve is adjusted,
5 is a view showing a swirl valve rotated in the other direction in the intake air control apparatus for a vehicle according to the first embodiment of the present invention,
6 is a graph showing a change in opening degree of an intake valve according to a rotation angle of a swirl valve in an intake air control apparatus for a vehicle according to a first embodiment of the present invention,
7 is a view showing a reference state in an intake air control apparatus for a vehicle according to a second embodiment of the present invention,
8 is a view illustrating a state in which the opening degree of the intake valve is adjusted by rotating the swirl valve in one direction in the intake air control apparatus of the vehicle according to the second embodiment of the present invention,
9 is a view showing a swirl valve rotated in the other direction in the intake air control apparatus for a vehicle according to the second embodiment of the present invention,
10 is a view illustrating a state in which the opening degree of the intake valve is adjusted by rotating the swirl valve in the other direction in the intake air control apparatus for a vehicle according to the second embodiment of the present invention,
11 is a graph showing the change in opening degree of the intake valve according to the rotation angle of the swirl valve in the intake air control apparatus for a vehicle according to the second embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a vehicle air intake control apparatus according to a preferred embodiment of the present invention will be described with reference to the accompanying drawings.

FIG. 1 is a view showing an intake and exhaust system equipped with an intake control device for a vehicle according to an embodiment of the present invention, and FIG. 2 is a view illustrating an intake flow path on which an intake control device for a vehicle according to an embodiment of the present invention is mounted FIG. 3 is a view showing a reference state of an intake air control apparatus for a vehicle according to a first embodiment of the present invention, and FIG. 4 is a view for explaining the intake control apparatus for a vehicle according to the first embodiment of the present invention, FIG. 5 is a view showing a state in which the swirl valve is rotated in the other direction in the intake control device for a vehicle according to the first embodiment of the present invention, and FIG. 6 is a cross- 1 is a graph showing a change in opening degree of an intake valve according to a rotation angle of a swirl valve in an intake air control apparatus for a vehicle according to a first embodiment of the present invention.

Referring to FIGS. 1 to 6, in the intake control device for a vehicle according to the first embodiment of the present invention, a flow pipe 112 through which an intake air flows is divided to form a plurality of divided flow paths 114, (114) are provided with an intake passage (110) provided so as to communicate with one another in the same combustion chamber; An intake valve 160 provided in the flow pipe 112 and adapted to adjust the opening of the flow pipe 112 according to the rotation angle; A swirl valve 170 provided on any one of the plurality of divided flow paths 114 and adapted to adjust the opening degree of the divided flow path 114 according to the rotation angle; And a cam plate 200 coupled with the swirl valve 170 and formed with a cam groove 210. The intake valve 160 is inserted into the cam groove 210 at a position spaced from the rotation axis 162 And at least a portion of the cam groove 210 is pivoted about the center axis of the intake valve 160 while sliding the insertion protrusion 166 in accordance with the rotation of the swallow valve 170, A first rotation section 212 for rotating the valve 160 can be formed.

The intake flow path 110 is formed such that the flow tube 112 through which the intake air flows is divided to form a plurality of divided flow paths 114 and the plurality of divided flow paths 114 communicate with one another in the same combustion chamber.

The intake flow path 110 becomes a flow path of the intake air flowing toward the engine 50. The intake passage 110 of the present invention is provided with a flow pipe 112 having a space therein and the flow pipe 112 is divided at the downstream side based on the flow of the intake air to form a plurality of divided flow passages 114.

The division of the flow tube 112 can be done in various ways. For example, the flow tube 112 may be branched to form a plurality of tubes. The pipe-shaped outer wall of the flow tube 112 is maintained as it is, and the partition wall extending in the longitudinal direction of the flow tube 112 is provided therein, A plurality of divided flow paths 114 may be formed in the flow tube 112.

1 and 2 schematically show that the flow tube 112 is branched into a plurality of tubes to form a divided flow passage 114. [ The intake passage 110 shown in FIGS. 1 and 2 is formed by dividing the downstream side of the flow pipe 112 into two divided flow passages 114 as an embodiment.

On the other hand, the engine 50 is provided with a plurality of combustion chambers, and a plurality of divided flow paths 114 are communicated with the combustion chambers corresponding to each other. That is, the intake air passing through each of the divided flow paths 114 is eventually mixed with each other in the respective combustion chambers.

On the other hand, the intake valve 160 is provided in the flow pipe 112 and is provided to adjust the opening degree of the flow pipe 112 according to the rotation angle. The intake valve 160 is also referred to as an ACV (Air Control Valve).

The intake valve 160 regulates the opening degree of the flow pipe 112 to adjust the amount of the intake air flowing in the flow pipe 112. Although the type and shape of the intake valve 160 may vary, in an embodiment of the present invention, a valve of the kind constituted by the valve plate 164 provided with the rotation axis 162 is presented.

3 to 5 show an intake valve 160 and a swirl valve 170 constituted by a rotating valve plate 164 as a first embodiment of the present invention as described above. The swirl valve 170 is also referred to as an SCV (Swirl Control Valve).

Specifically, the intake valve 160 and the swirl valve 170 are formed to have valve plates 164 and 174 having the same or substantially similar cross-sectional shape as the intake flow area at the point where the apparatus is mounted.

The valve plates 164 and 174 have their respective rotation axes 162 and 172 and are rotated about the rotation axes 162 and 172. When the longitudinal direction of the valve plates 164 and 174 is aligned with the flow direction of the intake air The flow path is completely opened (OPEN).

In the present invention, the opening degree means the degree of opening of the valve or the corresponding passage, and the larger the opening degree, the larger the flow area of the intake air. Also, the opening degree can be expressed by the closing amount, and the larger the closing amount, the smaller the flow area of the intake air. That is, as the opening degree is larger, the closing amount is expressed by a smaller value, which can be understood as a concept opposite to each other.

As the valve plates 164 and 174 rotate, the area through which the intake air can flow is gradually reduced, which can be expressed as the opening degree of the valve or the opening degree of the passage gradually decreases. (It can also be expressed that the amount of closing is increased.)

In the present invention, the intake valve 160 is provided in the flow pipe 112. That is, the intake valve 160 of the present invention is provided to control the flow rate of the intake air via the flow pipe 112. The position of the intake valve 160 is schematically shown in FIG. 1, and FIGS. 3 to 5 show cross sections of the intake valve 160 provided in the flow pipe 112.

In the present invention, a state in which the opening degree of the intake valve 160 is set to the maximum and the valve plate 164 and the valve plate 164 of the valve are aligned in parallel with the flow direction of the intake air, State ", and the rotation angle of the intake valve 160 and the swirl valve 170 in this reference state is defined as zero.

That is, the intake valve 160 and the swirl valve 170 shown in FIG.

On the other hand, the swirl valve 170 is provided in any one of the plurality of divided flow paths 114 and is provided to adjust the opening degree of the divided flow paths 114 according to the rotation angle.

Preferably, the intake valve 160 is located on the downstream side of the flow pipe 112, and the swirl valve 170 is disposed on the upstream side of the split flow passage 114 and adjacent to each other. This is advantageous in that the intake valve 160 and the swirl valve 170 interlock with each other to control the rotation angle.

The swirl valve 170 is positioned on one of the divided flow paths 114 and is different in position from the intake valve 160. Particularly, the swirl valve 170 is connected to any one of the plurality of divided flow paths 114 Thereby regulating the opening of the divided flow passage 114.

The swirl valve 170 is particularly used to form a swirl of the intake air flowing into the combustion chamber. As described above, the plurality of divided flow paths 114 communicate with each other in the same combustion chamber. The opening degree of one of the split-type circles 114 provided with the swirl valve 170 becomes 0 (the closing amount becomes the maximum) When the flow of the intake air is interrupted, only the intake air passing through the remaining divided flow paths 114 flows into the combustion chamber. At this time, the intake air flowing into the combustion chamber has an unbalanced flow inside the combustion chamber as compared with the state in which all the divided flow paths 114 are opened.

For example, as shown in Figs. 1 and 2, when two divided flow paths 114 are provided, when the intake air passing through the two divided flow paths 114 flows into the combustion chamber, When the intake air flows into the combustion chamber only through one of the divided flow paths 114, the intake air flowing toward the other divided flow path 114 does not flow, so that the balance against the intake flow in the combustion chamber The sludge disappears and the flow is deflected.

At this time, a swirl is induced in the combustion chamber by the deflected flow. For this reason, in the present invention, the valve provided in any one of the plurality of divided flow paths 114 is defined as the swirl valve 170. [ The direction of the intake flow into the combustion chamber or the mutual positional relationship can be variously determined.

When the degree of opening of the intake valve 160 decreases, the amount of intake air flowing into the combustion chamber decreases. However, when the opening degree of the swirl valve 170 decreases, a swirl is generated while the amount of intake air flowing into the combustion chamber is maintained substantially constant.

3 to 5 show the position of the swirl valve 170 provided on one of the two divided flow paths 114 as a first embodiment of the present invention, Respectively.

Meanwhile, the cam plate 200 is coupled to the swirl valve 170 and is rotatable together. The cam plate 200 is coupled to the swirl valve 170 and is rotatable around a rotation axis 172 of the swirl valve 170. Meanwhile, the material and shape of the cam plate 200 can be variously applied.

The cam plate 200 is provided with a cam groove 210. The cam groove 210 corresponds to a groove formed in the cam plate 200. The groove may be a groove passing through both sides of the cam plate 200, And may be provided in the shape of a recess embedded in one surface of the base 200. Further, the cam plate 200 may be formed as a single body, or a plurality of plates may be combined.

The cam plate 200 serves as a medium for transferring the power transmitted to the swirl valve 170 through the driving unit 140 through the cam groove 210 to the intake valve 160 and rotating the same .

The intake valve 160 is provided with an insertion protrusion 166 inserted into the cam groove 210 at a position spaced apart from the rotation shaft 162. At least a portion of the cam groove 210 rotates about the rotational axis 162 of the intake valve 160 while the insertion protrusion 166 slides along with the rotation of the cam plate 200 so that the intake valve 160 Thereby forming a first rotation section 212 to be rotated.

The intake valve 160 is provided with an insertion protrusion 166 at a position spaced apart from the rotation axis 162 so that the insertion protrusion 166 rotates together with the intake valve 160. The rotational axis of the insertion protrusion 166 is the same as the rotational axis 162 of the intake valve 160.

The insertion protrusion 166 is provided to be inserted into the cam groove 210. When the cam plate 200 rotates, the insertion protrusion 166 slides along the cam groove 210. At this time, depending on the extended shape of the cam groove 210, the insertion protrusion 166 sliding on the corresponding section is rotated around the rotation axis 162 of the intake valve 160.

Concretely, depending on the shape in which the cam groove 210 is extended, the side surface of the cam groove 210 presses the side surface of the insertion protrusion 166 together with the rotation of the swirl valve 170, so that the insertion protrusion 166 The position of the insertion protrusion 166 that merely slides does not change with respect to the rotational axis 172 of the swirl valve 170. The position of the insertion protrusion 166, )

That is, when the insertion protrusion 166 is inserted into the cam groove 210 and the cam plate 200 rotates, the insertion protrusion 166 is eventually slid along the cam groove 210. The sliding movement of the insertion protrusion 166 The rotation of the insertion protrusion 166 may lead to the rotation of the intake valve 160. [

The insertion protrusion 166 inserted into the cam groove 210 may slide according to the extended shape of the cam groove 210 but may not be rotated about the rotational axis 162 of the intake valve 160.

For example, when the cam groove 210 partially extends in a circular arc around the rotation axis 172 of the swirl valve 170, the insertion protrusion 166 that slides the cam groove 210 slides the intake valve 160, As shown in Fig. This will be described in detail below.

FIG. 3 shows a reference state in which the intake valve 160 is in the maximum open (OPEN) state and the swing angle of the swirl valve 170 is defined as zero. That is, the reference state of the present invention means a state in which the intake valve 160 is in the maximum open state, and the rotation angle of the intake valve 160 and the swirl valve 170 corresponding to the state is zero.

3, the opening of the intake valve 160 is maximized, and the insertion protrusion 166 is inserted into the cam groove 210. The length of the cam groove 210 may be determined in various ways. In the present invention, at least a portion of the cam groove 210 is provided to form a first rotation section 212 in which the insertion projection 166 is rotated while being slid.

FIG. 3 shows a first rotation section 212 in the cam groove 210. On the other hand, FIGS. 4 and 5 show a state in which the swirl valve 170 is rotated in one direction or the other direction from the reference state.

Particularly, FIG. 4 shows a state in which the swing valve 170 is rotated so that the insertion protrusion 166 is slid in the first rotation section 212. As will be described in detail below, one direction and the other direction of the rotation axis can be freely set in the present invention, and the clockwise direction is defined as one direction and the counterclockwise direction is defined as the other direction for ease of explanation.

4 is a state in which the swirl valve 170 is rotated clockwise around the rotation axis 172 in the state of FIG. 3, which can be expressed as a state in which the swirl valve 170 is rotated in one direction from the reference state . In the graph of Fig. 6, the one-way rotation of the swirl valve 200 is indicated in the (+) direction.

5 shows a state in which the swirl valve 170 is rotated in the counterclockwise direction, which may be a state in which the swirl valve 170 is rotated in the other direction from the reference state. In the graph of FIG. 6, the rotation of the swirl valve 200 in the other direction is indicated by (-) direction.

As described above, the one-direction and the other direction as described above are arbitrarily set for the purpose of explanation as described above, and may be mutually different. However, if the one direction and the other direction are set differently, it is preferable that the position of the first rotation section 212 and the relationships of (+) and (-) in FIG. 6 are changed accordingly.

As a result, in the present invention, at least a part of the cam groove 210 forms the first rotation section 212, so that the insertion projection 166 can be rotated in accordance with the rotation angle or direction of the swirl valve 170, .

In addition, in the first rotation section 212 of the cam groove 210, depending on the longitudinal direction setting of the cam groove 210, the insertion protrusion 212 slides on the first rotation section 212 with respect to the same rotation angle of the swirl valve 170, It is possible to increase or decrease the rotation angle of the motor 166.

That is, the present invention preferably includes a swirl valve 170 that is rotated by the driving unit 140, and the insertion protrusion 166 slides through the cam groove 210 formed in the swirl valve 170, Thus, by adjusting only the rotation angle of the driving unit 140, the rotation of the intake valve 160 and the amount of rotation can be controlled.

An example of the beneficial effect revealed through this scheme can be seen from FIG. Fig. 6 is a graph showing changes in the opening degree of the intake valve 160, which varies depending on the rotation angle of the swirl valve 170 shown in Fig.

As the swirl valve 170 is rotated from the reference state and the insertion protrusion 166 slides on the first rotation section 212, the insertion protrusion 166 rotates about the rotation axis 162 of the intake valve 160 The rotation angle of the swirl valve 170 and the opening degree change of the intake valve 160 are shown in FIG.

In the first embodiment of the present invention shown in FIG. 6, when the rotation angle of the swirl valve 170 is increased in one direction, the intake valve 160 is rotated and the opening degree is gradually decreased. In Fig. 6, the vertical axis is defined as a closing amount, which is an opposite concept of the opening degree, so that 100% of the vertical axis means the closing amount, and the opening degree of the corresponding point becomes zero. The closing amount of the intake valve 160 is shown by an ACV line.

The horizontal axis in FIG. 6 is the rotation angle of the swirl valve 170. The direction indicated by (+) signifies the unidirectional rotation angle of the swirl valve 170, and the direction indicated with (-) signifies the rotation angle of the swirl valve 170 in the other direction.

This definition is only one of various embodiments. If one direction is defined as a counterclockwise direction rather than a clockwise direction as described above, the one-directional rotation angle in the graph of FIG. The concept or content will not change.

6, when the rotational angle of the swirl valve 170 is 0, the closing amount of the intake valve 160 is gradually increased. This is because the swirl valve 170 rotates in one direction It means that the lower insertion projection 166 is sliding on the first rotation section 212.

When the swirl valve 170 is rotated in the other direction, it can be seen that the closing amount or opening degree of the intake valve 160 is not changed. By appropriately setting the shape of the cam groove 210, The rotation of the intake valve 160 and the rotation angle of the intake valve 160 can be variously adjusted.

The curvature or longitudinal direction of the cam groove 210 may be appropriately adjusted to form a correlation between the rotational angle of the swirl valve 170 and the rotational angle of the intake valve 160.

For example, if the curvature of the first rotation section 212 is appropriately adjusted, the amount of closing of the intake valve 160 becomes 100%, and the rotation angle of the intake valve 160 becomes about 90 °. ) Can be rotated only 30 degrees.

That is, by setting the curvature of the first rotation section 212 of the cam groove 210 so as to reduce the rotation angle of the swirl valve 170 and increase the relative rotation angle of the intake valve 160, The reactivity to the change can be greatly improved.

In other words, in the present invention, the swirl valve 170 is rotated through the single driving part 140 while the intake valve 160 is not directly rotated, and at the same time, the intake valve 160 is rotated in conjunction with the intake valve 160, It is possible to change the opening degree of the swirl valve 170 more simply and variously and change the opening degree of the various intake valves 160 without complicating the control by varying the rotation angle ratio.

1 and 2, in the intake control device for a vehicle according to an embodiment of the present invention, the plurality of divided flow paths 114 are branched to form a plurality of branched flow paths 116, And a flow path 116 is provided so as to communicate with a plurality of combustion chambers formed in the engine 50, respectively. Here, the branch passage 116 may be an intake manifold.

Specifically, in the present invention, a plurality of divided flow paths 114 are provided, and the divided flow paths 114 are branched to form a plurality of branched flow paths 116, respectively. Further, it is preferable that a plurality of branch flow paths 116 branched from any one of the divided flow paths 114 communicate with different combustion chambers.

As described above, the plurality of divided flow paths 114 of the present invention are communicated with one another in the same combustion chamber. The branched flow paths 116 branched from the different divided flow paths 114 of the branched flow paths 116, Respectively.

The embodiment of FIGS. 1 and 2 will be described below as an example. The number of divided flow paths 114 divided from the flow tube 112 may vary, but in the embodiment of the present invention, two divided flow paths 114 are formed from the flow tube 112.

On the other hand, each of the divided flow paths 114 is branched again on the downstream side to form the branched flow paths 116. The number of the branched flow paths 116 branched by one divided flow path 114 may vary, Four branch flow paths 116 are formed for each of the divided flow paths 114. In this embodiment,

A plurality of branch flow paths 116 branched from any one of the divided flow paths 114 are preferably provided to communicate with different combustion chambers. In the embodiment shown in FIGS. 1 and 2, four branch flow paths 116 ) Communicate with four different combustion chambers, respectively.

In such a case, the branch flow paths 116 formed from the different divided flow paths 114 communicate with the same combustion chamber, respectively, so that the plurality of divided flow paths 114 are communicated with the respective combustion chambers.

As a result, the intake flow path 110 of the present invention is configured such that the divided flow paths 114 are branched so as to form a plurality of divided flow paths 116 and the branched flow paths 116 branched from the respective divided flow paths 114 are connected to the engine 50, The branched flow paths 116 branched from the different divided flow paths 114 communicate with the same combustion chamber so that the plurality of divided flow paths 114 communicate with one another in the same combustion chamber.

According to the embodiment of the present invention as described above, the swirl valve 170, which is provided on one of the divided flow paths 114 and adjusts the intake amount of the divided flow path 114, The intake air amount can be adjusted.

Further, even when the swirl valve 170 is provided as a single object, a swirl is induced in the entire combustion chamber of the engine 50 when the swirl valve 170 reaches the maximum closing amount.

According to the above structure, a swirl can be induced in a plurality of combustion chambers through a single swirl valve 170 despite the provision of a plurality of combustion chambers, thereby simplifying the structure, reducing the weight and reducing the cost. .

On the other hand, it is obvious that the amount of intake air is adjusted in the entire combustion chamber of the engine 50 by adjusting the opening degree of the intake valve 160 existing in the flow pipe 112.

3 to 4, in the intake control device for a vehicle according to the embodiment of the present invention, the first rotation section 212 of the cam groove 21 is connected to the rotation axis of the swirl valve 170 The insertion protrusion 166 is slid on the first rotation section 212 and rotated.

Specifically, the distance between the rotation axis 172 of the swirl valve 170 and the cam groove 210 varies along the longitudinal direction of the first rotation section 212. In other words, the first rotation section 212 is formed so as to form an out-of-arc curve about the rotation axis 172 of the swirl valve 170.

At this time, the rotation angle of the intake valve 160 is changed according to the degree of change of the distance of the swirl valve 170 with respect to the rotation axis 172 along the longitudinal direction of the first rotation section 212. For example, as the distance of the swirl valve 170 from the rotation axis 172 of the first rotation section 212 to the rotation axis 172 of the swirl valve 170 varies greatly along the longitudinal direction, the amount of change in the rotation angle of the intake valve 160 in the corresponding section increases .

At this time, the determination as to whether the distance change of the first rotation section 212 is close to or away from the rotation axis 172 of the swirl valve 170 can be determined according to the rotation direction of the insertion projection 166 at the position.

For example, in the case of FIG. 3, the first rotation section 212 has a shape extending away from the rotation axis 172 of the swirl valve 170 as the length of the first rotation section 212 is increased. This is because the insertion protrusion 166 is positioned to rotate in a direction away from the rotation axis 172 of the swirl valve 170 in the first rotation section 212. If the position characteristic of the insertion protrusion 166 The swirl valve 170 is rotated in a direction in which the swirl valve 170 is rotated so that the first rotation section 212 is extended toward the rotation axis 172 of the swirl valve 170, (Since the insertion protrusion 166 can no longer be pivoted so as to be closer to the rotation axis 172 of the swirl valve 170).

The first rotation section 212 is extended so that the distance between the rotation axes 172 of the swirl valve 170 changes along the longitudinal direction so that when the swirl valve 170 rotates, the insertion projection 166 is rotated in the first rotation section The side wall of the first rotation section 212 presses the side surface of the insertion projection 166 so that the insertion projection 166 is rotated about the rotation axis 162 of the intake valve 160 , Whereby the intake valve 160 is rotated. FIG. 4 shows a state of the insertion protrusion 166 rotated by sliding the first rotation section 212 in the state of FIG.

3, 4 and 6, in the intake control device for a vehicle according to the first embodiment of the present invention, the first rotation section 212 includes an intake valve 160 by the insertion protrusion 166 to be slid, Is provided in a bent shape so as to be uniformly arranged with respect to the rotation angle of the swirl valve (170).

As described above, the first rotation section 212 of the cam groove 210 can adjust the rotation angle of the insertion protrusion 166 in the corresponding section according to the change of the distance to the rotation axis 172 of the swirl valve 170. In the first embodiment of the present invention, the rotation angle of the insertion protrusion 166 in the first rotation section 212 with respect to the rotation angle of the swing valve 170 is changed to the first rotation section 212 of the swirl valve 170 with respect to the rotary shaft 172 is set.

The shape determination of the first rotation section 212 may be performed in various manners. For example, it may be determined through theoretical prediction, or a desired shape may be obtained by simulating the modeled image.

However, the position at the time when the insertion projection 166 enters the first rotation section 212 plays an important role in the determination of the first rotation section 212. Specifically, it is as follows.

The insertion protrusions 166 correspond to the rotors fixed to the intake valves 160. [ That is, the insertion protrusion 166 always has a constant distance from the rotation axis 162 of the intake valve 160 and rotates about the rotation axis 162 of the intake valve 160.

The distance between the insertion protrusion 166 and the rotary shaft 172 of the swirl valve 170 can be changed but the distance from the rotary shaft 162 of the intake valve 160 is always constant. The distance to the rotation axis 172 can also be changed within a certain range, and it does not change without limitation. This is because the intake valves 160 and the rotary shafts 162 and 172 of the swirl valve 170 have fixed positions.

The following description will be made with reference to FIG. In the first embodiment shown in FIG. 4, an insertion protrusion 166 sliding along the first rotation section 212 is positioned to face the cam plate 200 with respect to the intake valve 160.

At this time, when the insertion protrusion 166 is pivoted, the insertion protrusion 166 will rotate mainly away from the cam plate 200. [ This can be confirmed from the position of the insertion protrusion 166 of FIG. 4 changed from FIG.

That is, in the first embodiment as shown in FIG. 4, the insertion protrusions 166 are rotated away from the cam plate 200 in the first rotation section 212, so that the first rotation section 212 is swirled along the longitudinal direction Away from the rotary shaft 172 of the valve 170. [ The shape of the first rotation section 212 is shown in Figs. 3 and 4. Fig.

3 to 4, when the insertion protrusion 166 that slides on the first rotation section 212 is located on the upstream side (left side in the drawing) of the intake valve 160, the insertion protrusion 166 The first rotation section 212 is moved toward the rotation axis 172 of the swirl valve 170 along the longitudinal direction by the rotation of the swirl valve 170. In this case, Shape. That is, the change in the longitudinal direction of the first rotation section 212 depends on the position of the insertion projection 166 at that time.

In this case, the curvature or the extended shape formed by the first rotation section 212 can be determined from a design point of view. In the first embodiment of the present invention, the rotation angle of the intake valve 160 is determined by the swirl valve 170 The curvature is determined so as to form a constant ratio with respect to the rotation angle.

These results can be confirmed from FIG. 6 shows that the closing amount of the intake valve 160 becomes 100% when the rotation angle of the swirl valve 170 is rotated by 30 degrees in one direction as one of various embodiments of the present invention.

When the closing amount of the intake valve 160 is 100%, it means that the rotation angle is preferably 90 degrees. 6 shows that the inclination of the intake valve 160 is constant. The reason for this is that the rotation angle of the intake valve 160 is increased at a constant ratio with respect to the rotation angle of the swirl valve 170 It means.

It should be noted that the rotation angle ratio of the intake valve 160 to the rotation angle of the swirl valve 170 shown in FIG. 6 is only one of various embodiments, and the ratio can be variously determined as needed. something to do.

As a result, in the embodiment of the present invention, the curvature of the first rotation section 212 is set so that the rotation angle of the intake valve 160 is uniform with respect to the rotation angle of the swirl valve 170, Accordingly, it is easy to accurately control the opening or closing amount or the rotation angle of the intake valve 160.

3, 5 and 6, in the intake control device for a vehicle according to the first embodiment of the present invention, the cam groove 210 has an insertion portion (not shown) A non-rotating section 214 having a constant distance from the rotation axis 202 of the cam plate 200 along the longitudinal direction is formed so that the projection 166 is not rotated.

As described above, in the embodiment of the present invention, as the distance of the swirl valve 170 from the rotation axis 172 is changed, the side wall of the swirl valve 170 presses the side surface of the insertion protrusion 166 If the distance between the cam groove 210 and the rotation axis 172 of the swirl valve 170 is constant along the longitudinal direction of the cam groove 210, The pressing projection 166 is not pressed, and the insertion projection 166 does not rotate.

In the embodiment of the present invention, at least a portion of the cam groove 210 is maintained at a constant distance from the rotation axis 172 of the swallow valve 170 so that the insertion protrusion 166, which slides, ).

In the embodiment of the present invention, even when the swirl valve 170 is rotated, since the opening degree of the intake valve 160 is kept constant, a non-rotating section is provided, The intake flow control can be satisfied.

For example, when the operation of the other mechanism is controlled through the swirl valve 170, the swirl valve 170 is rotated for the control of the other mechanism. At this time, when the intake valve 160 is required to maintain the opening degree May be required.

The first embodiment of the present invention may be especially useful in such situations. The degree of freedom of the control of the opening degree of the intake valve 160 using the swirl valve 170 is greatly improved because the opening degree of the intake valve 160 is maintained even when the swirl valve 170 is rotated.

5 shows a situation in which the insertion protrusion 166 is located in the non-rotating section 214. [ 5, the swirl valve 170 rotates while the intake valve 160 rotates in the state shown in FIG. 5, and the swirl valve 170 rotates from the reference state shown in FIG. It can be confirmed that the reference state is maintained.

6, although the swing angle of the swirl valve 170 changes, the opening degree of the intake valve 160 may be maintained constant, and the interval between the swing valve 170 and the swing valve 170 may be determined such that the insertion protrusion 166 is in the non- 214, respectively.

As a result, according to the present invention, since the rotation section 212 and the non-rotation section 214 are provided in the cam groove 210, the rotation of the insertion projection 166 and the rotation angle change rate The degree of freedom is greatly improved in terms of control.

3 to 6, in the intake control device for a vehicle according to the embodiment of the present invention, the swirl valve 170 is moved in one direction from the reference state corresponding to the maximum open (OPEN) state of the intake valve 160 The cam groove 210 of the cam plate 200 is provided so that the insertion protrusion 166 is positioned on the first rotation section 212 and the split flow passages 114 provided with the swirl valve 170 therein The rotary groove 118 may be formed such that the swirl valve 170 can be further rotated in one direction from the set angle.

As described above, in the present invention, the one direction and the other direction are determined either clockwise or counterclockwise. In other words, if the clockwise direction is set to one direction, the other direction is counterclockwise.

In addition, the one direction may be set to the clockwise direction or the counterclockwise direction. This is a matter of arbitrary decision. 3 to 6 show an embodiment in which one direction is set to clockwise.

Meanwhile, in the embodiment of the present invention, when the swirl valve 170 is rotated in one direction from the reference state, the cam groove 210 is provided so that the insertion protrusion 166 is positioned in the first rotation section 212.

That is, in the reference state, the insertion protrusion 166 is positioned at the end of the first rotation section 212 in the cam groove 210, so that when the swirl valve 170 is rotated in one direction, the insertion projection 166 is rotated in the first rotation section 212).

The shape of this cam groove 210 is shown in Figs. When the swirl valve 170 rotates in one direction from the reference state, the cam groove 210 has a section in which the insertion protrusion 166 is positioned in the first rotation section 212.

The state in which the swirl valve 170 is rotated in one direction from the reference state in Fig. 3 is shown in Fig. 4, when one direction is set to the clockwise direction as one of various embodiments of the present invention, the swirl valve 170 rotates in one direction, and at the same time, the insertion protrusion 166 rotates in the first rotation period 212, the opening degree of the intake valve 160 is changed.

The present invention further includes a rotation groove 118 in which the valve plate 174 of the swirl valve 170 can rotate with the divided flow paths 114 provided with the swirl valve 170.

4, when the swirl valve 170 is rotated in one direction in the reference state in which the closing amount is zero, the valve plate 174 is clogged with the inner wall of the divided flow passage 114, . However, according to the present invention, the swirl valve 170 can be further rotated in one direction in the reference state by securing the area in which the valve plate 174 of the swirl valve 170 is rotatable inside the split flow passage 114. However, it can be determined that the split flow path 114 still maintains the maximum open (OPEN) state.

The cam groove 210 is provided so that the insertion protrusion 166 slides on the first rotation section 212 in the unidirectional rotation of the swallow valve 170, Only the opening degree of the intake valve 160 among the valve 160 and the swirl valve 170 can be adjusted. (This is because the swirl valve 170 rotates in one direction, but the opening degree maintains the maximum open state.)

6, in the unidirectional rotation of the swirl valve 170 indicated by (+) direction, the closing amount of the intake valve 160 gradually increases, but the closing amount of the swirl valve 170 is maintained at 0% Can be confirmed. The closing amount of the swirl valve 170 is indicated by an SCV line.

3 to 6, in the intake control device for a vehicle according to the embodiment of the present invention, when the swirl valve 170 is rotated in the other direction from the reference state, the cam groove 210 of the cam plate 200 is inserted The projection 166 is provided so as to be positioned on the non-rotating section 214.

In the embodiment of the present invention, when the swirl valve 170 is rotated in the other direction from the reference state, the cam groove 210 is provided so that the insertion protrusion 166 is positioned in the non-rotation section 214.

That is, in the reference state, the insertion protrusion 166 is positioned at the end of the non-rotation section 214 in the cam groove 210 so that when the swirl valve 170 is rotated in the other direction, the insertion projection 166 is rotated in the non-rotation section 214 .

Meanwhile, in the embodiment of the present invention, preferably, the insertion protrusion 166 is positioned at the boundary between the first rotation section 212 and the non-rotation section 214 in the reference state.

The shape of this cam groove 210 is shown in Figs. 3-5. When the swirl valve 170 rotates from the reference state to the other direction, the cam groove 210 has a section in which the insertion protrusion 166 is located in the non-rotation section 214.

The state in which the swirl valve 170 is rotated in the other direction from the reference state in Fig. 3 is shown in Fig. 5, when the swing valve 170 rotates in the other direction and the insertion protrusions 166 are rotated in the counterclockwise direction as one of the first embodiment of the present invention, And the opening degree of the intake valve 160 is maintained as it is slid in the rotation section 214. Preferably, since the insertion projection 166 slides on the non-turning section 214 from the reference state, the intake valve 160 maintains the maximum opening state.

The cam groove 210 is provided to slide the insertion projection 166 in the non-rotation section 214 when the swirl valve 170 is rotated in the other direction, so that the rotation of the swirl valve 170 in the other direction Only the opening degree of the swirl valve 170 among the intake valve 160 and the swirl valve 170 can be adjusted.

That is, in the first embodiment of the present invention, a plurality of valves can be individually controlled according to the rotational direction of the swirl valve 170, which is very advantageous. This has the effect that a complicated control system is not required, the number of necessary driving units 140 is reduced, and furthermore, the stable intake valve 160 and the swirl valve 170 can be controlled.

6, in the unidirectional rotation of the swirl valve 170 indicated by (+) direction, the closing amount of the intake valve 160 gradually increases, but the closing amount of the swirl valve 170 is maintained at 0% The closing amount of the intake valve 160 is maintained at 0% while the swirl valve 170 is rotated in the other direction, but the closing amount of the swirl valve 170 is gradually increased Can be confirmed. As described above, it is needless to say that the rotation direction of the swirl valve 170 and the rotation angle change rate of the intake valve 160 and the swirl valve 170 can be variously determined.

3 shows a K line which is a virtual reference line for the swing valve 170 rotation angle change. That is, the K line is a line indicating a state in which the rotation angle of the swirl valve 170 is zero.

FIG. 4 shows a state in which the swirl valve 170 is rotated in one direction in the reference state of FIG. At this time, a K 'line showing the degree to which the swirl valve 170 is rotated in one direction is shown. The angle of rotation in which the swirl valve 170 is rotated from the reference state is the same as the angle formed by the K line and the K 'line.

FIG. 5 shows a state in which the swirl valve 170 is rotated in the other direction in the reference state of FIG. Referring to the line K ', it is possible to confirm how much the swirl valve 170 is rotated in the other direction.

3 to 6, in the intake air control apparatus for a vehicle according to the first embodiment of the present invention, the rotation section 212 has a rotation angle of the intake valve 160 by the insertion protrusion 166, And is formed in a bent shape so as to have a constant ratio with respect to the rotation angle of the swirl valve (170).

As described above, the first rotation section 212 can determine the rotation angle according to the sliding of the insertion projection 166 by setting the curvature. In the first embodiment of the present invention, in particular, the curvature of the first rotation section 212 is adjusted so as to be uniform between the rotation angle of the swirl valve 170 and the rotation angle of the intake valve 160 and the swirl valve 170 .

The shape of the first rotation section 212 is shown in Figs. 3 to 5. Fig. The ratios of the intake valves 160 with the swirl valve 170 on the rotation angle may be different from each other, but the ratios are kept constant with rotation.

FIG. 6 shows a change in the closing amount of the intake valve 160 and the swirl valve 170, which is changed by the first rotation section 212 having the above-described characteristics. 6, it can be seen that the closing amount of the intake valve 160 is increased when the rotation angle of the swirl valve 170 is increased in one direction (+ direction). At this time, the change in the amount of closing of the intake valve 160, Is constant.

In addition, it can be seen that the swirl amount of the swirl valve 170 increases when the swirl angle of the swirl valve 170 is increased in the other direction (-) direction. The swirl amount change of the swirl valve 170 at this time, .

As a result, the first embodiment of the present invention is configured such that the intake valve 160 by the first rotation section 212 is changed to maintain a constant maintenance ratio with respect to the rotation angle of the swirl valve 170, And the control accuracy with respect to the swirl valve 170 can be improved.

As shown in FIGS. 1, 3 to 6, in the intake control device for a vehicle according to the first embodiment of the present invention, a driving unit 140 for providing rotational force to the swirl valve 170; And a control unit 150 for controlling the rotation angle of the swirl valve 170 by controlling the driving unit 140. The control unit 150 controls the rotation angle of the swirl valve 170 based on the regeneration mode of the DPF unit 104 provided on the exhaust flow path 70, The rotation angle of the swirl valve 170 is adjusted so that the insertion protrusion 166 slides in the first rotation section 212 while the opening degree of the swirl valve 170 is adjusted within the rotation groove 118 .

Specifically, the swirl valve 170 is provided with a rotational force by the driving unit 140. As described above, the driving unit 140 may have various types and operating modes. For example, the driving unit 140 may be operated in a negative pressure mode, and preferably, a motor type that facilitates the control of the rotation angle of the swirl valve 170 may be provided.

Meanwhile, the control unit 150 is provided in the first embodiment of the present invention. The control unit 150 controls the rotation angle of the swirl valve 170 by controlling the operation of the driving unit 140. The control unit 150 adjusts the opening degree of the intake valve 160 and the swirl valve 170 according to the driving conditions of the vehicle so that the flow condition of the intake air satisfies the vehicle driving environment.

On the other hand, in the first embodiment of the present invention, the DPF apparatus 104 is provided on the exhaust passage 70. The DPF device 104 is a device for removing carbon substances or particulate matter (PM), particularly in the incompletely combusted state, among the toxic substances contained in the exhaust of the vehicle.

However, the DPF apparatus 104 according to the first embodiment of the present invention collects PM during exhaust and, when the amount of collected PM becomes a limit amount or more, the PM is burned Or the like in a manner such that they can be reproduced.

On the other hand, when the DPF unit 104 is in the regeneration mode, the controller 150 reduces the opening degree of the intake valve 160, and the swirl valve 170 rotates the swirl valve 170 to maintain the opening degree. In particular, in the embodiment of the present invention, the swirl valve 170 is rotated in one direction to satisfy the valve opening condition.

In the regeneration mode of the DPF apparatus 104 according to the embodiment of the present invention, the amount of intake air is reduced to increase the combustion material (for example, unburned fuel, etc.) during the exhaust so that the combustion operation in the DPF apparatus 104 occurs.

The control unit 150 controls only the rotation angle of the swirl valve 170 without adjusting the opening degree of each of the intake valve 160 and the swirl valve 170 so that the intake valve 160 and the swirl valve 170, All of the rotation angles required for the valve 170 can be satisfied.

In particular, as described above, in the embodiment of the present invention, the controller 150 rotates the swirl valve 170 in one direction. At this time, the rotation angle of the swirl valve 170 may be determined as various values and may be determined through various parameters in the driving environment.

When the swirl valve 170 is rotated in one direction, the insertion protrusion 166 slides the first rotation section 212 in the cam groove 210, so that the opening degree of the intake valve 160 is reduced. The opening degree of the swirl valve 170 is set such that the valve plate 174 rotates within the rotation groove 118, and is maintained at the maximum value continuously.

FIG. 1 shows a DPF apparatus 104 provided on an exhaust flow path 70 according to an embodiment of the present invention. 4, the control unit 150 operates the driving unit 140 to rotate the swirl valve 170 in one direction, so that the opening degree of the intake valve 160 is increased And the opening degree of the swirl valve 170 is shown as being maintained at the maximum.

Accordingly, the amount of intake air flowing into the engine 50 is reduced, but no swirl is generated, so that the ratio of the unburned fuel material and the like is increased during the exhaust, and the DPF device 104 is controlled to be in the regeneration mode of the DPF device 104, Is reproduced.

6 is a graph showing a situation in which the opening degree of the intake valve 160 is reduced and the opening degree of the swirl valve 170 is maintained by rotating the swirl valve 170 in one direction.

The control unit 150 controls the single swirl valve 170 through only one driving unit 140 so that the intake valve 160 for meeting the regeneration mode of the DPF unit 104 can be controlled, The opening degree of the swirl valve 170 and the opening degree of the swirl valve 170 can all be satisfied.

1, 3, 5, and 6, in the intake air control apparatus for a vehicle according to the first embodiment of the present invention, the control unit 150 determines whether or not the vehicle is in the normal mode, The opening degree of the intake valve 160 is maintained while the opening degree of the swirl valve 170 is adjusted by adjusting the rotation angle of the swirl valve 170 so that the projection 166 slides in the non-rotation section 214 of the cam groove 210 .

In the embodiment of the present invention, the normal mode is a mode in which regeneration of the DPF device 104 or the LNT device 102 or the like provided on the exhaust passage 70 of the vehicle is not required, It means the situation.

At this time, the controller 150 maintains the opening degree of the intake valve 160 to maintain the intake amount flowing into the engine 50 at a constant level. By controlling the opening degree of the swirl valve 170, the control unit 150 induces the swirl of the combustion chamber, . That is, the control unit 150 controls the intake valve 160 and the swirl valve 170 to increase the fuel combustion efficiency of the combustion chamber in a normal driving situation of the vehicle.

To this end, the controller 150 rotates the swirl valve 170 in the other direction. As described above, when the swirl valve 170 is rotated in the other direction, the insertion protrusion 166 slides in the non-rotating section 214 of the cam groove 210 to maintain the opening degree of the intake valve 160, 170 are rotated in the other direction to adjust the opening degree. At this time, the swirl valve 170 is preferably controlled so as to decrease the opening degree from the reference state which is the maximum opening state.

1 shows a control unit 150 for adjusting a rotation angle of the swirl valve 170 through a driving unit 140. An intake valve 160 and a swirl valve 170 are shown in FIG. 5, the swirl valve 170 is rotated in the other direction from the reference state to maintain the opening degree of the intake valve 160 while the opening degree of the swirl valve 170 is reduced from the reference state.

6, when the swirl valve 170 is rotated in the other direction by the controller 150, the closing amount of the swirl valve 170 is increased and the closing amount of the intake valve 160 is preferably maintained at 0% .

As a result, when the intake valve 160 maintains the opening degree and the opening degree of the swirl valve 170 is adjusted to meet the swirl induction level required in the combustion chamber according to the running condition of the vehicle, 150 can control the opening angle of the intake valve 160 and the swirl valve 170 according to the requirements by controlling only the rotation angle of one swirl valve 170 through the driving unit 140, There is an advantageous effect of satisfying the driving situation.

7 to 10, in the intake control device for a vehicle according to the second embodiment of the present invention, the cam groove 210 includes a first rotation section 212, at least some sections excluding the non-rotation section 214, A second rotation section 216 is formed in which the insertion protrusion 166 is rotated while being rotated according to the rotation of the swirl valve 170. The second rotation section 216 is rotated between the first rotation section 212 and the second rotation section 216, Section 214 is located.

The cam groove 210 may include a first rotation section 212 and a non-rotation section 214 as well as a second rotation section 216 for rotating the insertion protrusion 166 to be slid, .

The characteristic of the second rotation section 216 is not largely different from that of the first rotation section 212. That is, the second rotation section 216 is preferably provided to change the distance from the rotation axis 172 of the swirl valve 170 to rotate the insertion projection 166. At this time, the rotation of the second rotation section 216 And the like can be variously determined through the positional relationship of the insertion protrusions 166 and the like.

The cam groove 210 is formed such that the non-rotation section 214 is positioned between the first rotation section 212 and the second rotation section 216. That is, the insertion protrusion 166 slides in one of the first rotation section 212 and the second rotation section 216 according to the rotation of the swirl valve 170 in one direction or the other direction.

The opening degree of the intake valve 160 and the swirl valve 170 may vary depending on the driving condition of the vehicle. In a situation where the intake valve 160 maintains the maximum opening degree and the opening degree change needs to be made in a specific situation Can be.

For example, if the opening degree of the intake valve 160 and the swirl valve 170 are different from each other in accordance with the rotation direction of the swirl valve 170 as in the second embodiment of the present invention, The swirl valve 170 is rotated while the swirl valve 170 and the intake valve 160 are rotated at a predetermined rotation angle while the swirl valve 170 is rotated while the swirl valve 170 is rotated. Is to be rotated together.

As a result, in the second embodiment of the present invention, when the rotational angle of the intake valve 160 and the swirl valve 170 is adjusted through the two rotational directions, the rotational angle of the intake valve 160 and the swirl valve 170 There is an advantageous effect that various control situations can be realized.

In the embodiment in which the second rotation section 216 is formed as the second embodiment of the present invention, the second rotation section 216 in which the insertion projection 166 is rotated, as compared with the embodiment of Figs. They are substantially similar to each other in other features, and share technical features and ideas.

7 to 10, in the intake air control apparatus for a vehicle according to another embodiment of the present invention, when the swallow valve 170 moves from the reference state corresponding to the maximum open state of the intake valve 160 The cam groove 210 of the cam plate 200 is provided so that the insertion protrusion 166 is positioned on the non-rotation section 214 or the second rotation section 216. [

The swing valve 170 rotates in the other direction so that the insertion protrusions 166 are moved in the non-swinging section 214 or the second swinging section 216 of the cam groove 210 Sliding.

The non-rotating section 214 must be positioned between the first rotating section 212 and the second rotating section 216. Therefore, when the swirl valve 170 is rotated in the other direction from the reference state, The protrusion 166 slides on the non-rotating section 214 and then enters the second rotating section 216.

That is, in the second embodiment of the present invention, when the swirl valve 170 is rotated in one direction, the insertion protrusion 166 slides on the first rotation section 212 of the cam groove 210 to open the intake valve 160 . As a result, in the unidirectional rotation of the swirl valve 170, the swirl valve 170 can adjust only the opening degree of the intake valve 160 while maintaining the open state.

In the second embodiment of the present invention, when the swirl valve 170 is rotated in the other direction, the insertion protrusion 166 slides the non-rotating section 214 of the cam groove 210 at the beginning of rotation, The opening degree of the swirl valve 170 is rotated in the other direction and the opening degree is adjusted. That is, when the swirl valve 170 rotates in the other direction, the opening degree of the swirl valve 170 can be adjusted while maintaining the opening degree of the intake valve 160 at a certain rotation angle or less.

In the second embodiment of the present invention, when the swirl valve 170 is rotated so as to have a rotation angle of a predetermined level or more in the other direction, the insertion protrusion 166 moves in the second rotation section 216 of the cam groove 210 The opening degree of the intake valve 160 is adjusted, and the opening degree of the swirl valve 170 is also adjusted.

That is, when the rotation of the swirl valve 170 in the other direction is equal to or greater than a predetermined rotation angle, the opening degree of the intake valve 160 and the swirl valve 170 can be simultaneously controlled.

7 shows a reference state of the swirl valve 170 in the second embodiment of the present invention, and a K line which is a virtual reference line for the swing angle change of the swirl valve 170 is shown. That is, the K line is a line indicating a state in which the rotation angle of the swirl valve 170 is zero.

FIG. 8 shows a state in which the swirl valve 170 is rotated in one direction in the reference state of FIG. The opening degree of the intake valve 160 is reduced but the opening degree of the swirl valve 170 is maintained. At this time, a K 'line showing the degree to which the swirl valve 170 is rotated in one direction is shown. The angle of rotation in which the swirl valve 170 is rotated from the reference state is the same as the angle formed by the K line and the K 'line.

FIG. 9 shows a state in which the swirl valve 170 is rotated in the other direction in the reference state of FIG. The opening degree of the intake valve 160 is maintained but the opening degree of the swirl valve 170 is reduced. Referring to the line K ', it is possible to check whether the swirl valve 170 is rotated in the other direction.

FIG. 10 shows a state in which the swirl valve 170 is further rotated in the other direction and the insertion protrusion 166 is slid on the second rotation section 216 as shown in FIG. The opening degree of the intake valve 160 and the swirl valve 170 are reduced together.

The rotation angle of the swirl valve 170 is further increased so that the insertion protrusion 166 is moved in the second direction from the K 'line indicating the rotation angle of the swirl valve 170 in a state where the insertion projection 166 slides on the non- A line K " indicating the swirl angle of the swirl valve 170 in a state of sliding on the rotation section 216 is displayed.

7 to 11, in the intake control device for a vehicle according to the second embodiment of the present invention, a driving unit 140 for providing rotational force to the swirl valve 170; And a control unit 150 for controlling the rotation angle of the swirl valve 170 by controlling the driving unit 140. The control unit 150 controls the rotation angle of the swing valve 170 in the regeneration mode of the LNT apparatus 102 provided on the exhaust passage 70, The rotation angle of the swirl valve 170 is adjusted so that the insertion protrusion 166 slides in the second rotation section 216 and the rotation of the insertion protrusion 166 in the regeneration mode of the DPF apparatus 104 provided on the exhaust passage 70 The swirl valve 170 is adjusted so that the opening degree of the swirl valve 170 is adjusted within the range of the rotation groove 118. In this case,

Specifically, in the second embodiment of the present invention, an LNT device 102 for removing harmful substances in the exhaust gas is provided on the exhaust passage 70. The LNT device 102 can be used primarily to reduce incompletely burned nitrogen oxides during exhaust.

The regeneration mode of the LNT apparatus 102 is set in the control unit 150. In the regeneration mode of the LNT apparatus 102, it is required that the intake air amount is reduced and the swirl is induced in the combustion chamber. This may have the effect of reducing the incompletely burnt nitrogen oxide in exhaust during the regeneration process of the LNT apparatus 102 itself.

Meanwhile, in order to reduce the intake air amount and induce the swirl in the regeneration mode of the LNT apparatus 102, it is required to reduce the opening degree of the intake valve 160 and the swirl valve 170 simultaneously from the reference state. To this end, Controls the swing angle so that the swinging valve 170 is rotated in the other direction, in particular, the insertion protrusion 166 slides on the second rotation section 216 of the cam groove 210.

As described above, the situation in which the insertion protrusion 166 slides on the second rotation section 216 is that the intake valve 160 and the swirl valve 170 are both opened and closed due to the rotation of the swirl valve 170 in the other direction .

The control unit 150 rotates the swirl valve 170 so that the insertion protrusion 166 slides on the second rotation section 216 when the regeneration mode of the LNT apparatus 102 is started so that the intake valve 160 and the swirl The opening degree of the valve 170 is made smaller than the reference state so as to satisfy the requirement of the regeneration mode of the LNT apparatus 102.

The LNT apparatus 102 provided on the exhaust passage 70 is shown in Fig. 1 and is configured to swallow the swallow valve 170 such that the insertion projection 166 slides on the second rotation section 216 from the reference state shown in Fig. Fig.

Referring to FIG. 11, when the swirl valve 170 is rotated in the opposite direction to a predetermined level, the closing amount of the intake valve 160 and the swirl valve 170 is simultaneously adjusted. The rotation angle of the swirl valve 170, at which the specific closing amount change rate of the intake valve 160 and the swirl valve 170 and the opening degree of the intake valve 160 and the swirl valve 170 start to change at the same time, As shown in FIG.

According to the intake control device of the vehicle constructed as described above, it is possible to effectively operate a plurality of valves that regulate the intake flow while simplifying the structure.

Further, by driving the intake valve through the swirl valve, the degree of freedom of operation of the valve can be improved, for example, by adjusting the rotational angle ratio between the driving portion and the valve or keeping the valve in the non-rotating state despite the driving portion.

In addition, the cam plate can be transmitted to the intake valve by the rotational force transmitted to the swirl valve according to the shape of the cam groove, so that the plurality of valves can be operated as a single driving unit, thereby simplifying the structure and reducing weight.

In addition, the plurality of valves can be adjusted by a single driving unit according to the running state of the vehicle through the control unit, so that the intake flow according to the running state can be effectively satisfied.

Further, it is not necessary to simplify the cam groove shape and to apply the insertion projection structure to the swirl valve, so that the swirl valve can be simply manufactured in a simple structure.

While the present invention has been particularly shown and described with reference to specific embodiments thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the following claims It will be apparent to those of ordinary skill in the art.

50: engine 70:
102: LNT device 104: DPF device
110: intake air flow passage 112:
114: split flow path 116:
118: Rotary groove
140: driving unit 150:
160: intake valve 162: intake valve rotary shaft
164: intake valve valve plate 166: insertion projection
170: Swirl valve 172: Swirl valve rotating shaft
174: Swirl valve valve plate
200: cam plate 210: cam groove
212: first rotation section 214: non-rotation section
216: second turning section

Claims (12)

An intake flow passage provided so that a flow tube through which the intake air flows is divided to form a plurality of divided flow paths, and a plurality of divided flow paths are communicated with one another in the same combustion chamber;
An intake valve provided in the flow pipe, the intake valve being provided to adjust the opening degree of the flow pipe according to the rotation angle;
A swirl valve provided on any one of the plurality of divided flow paths and adapted to adjust the opening of the divided flow path according to the rotation angle; And
And a cam plate rotatably coupled with the swirl valve and having a cam groove,
The intake valve is provided with an insertion protrusion inserted into the cam groove at a position spaced from the rotation axis. At least a part of the cam groove is rotated about the central axis of the intake valve while the insertion protrusion is slid as the swirl valve rotates, And a second rotation section for rotating the first rotation section. The method according to claim 1,
Wherein the plurality of divided flow paths are each branched to form a plurality of branched flow paths, and a plurality of branch flow paths are provided so as to communicate with a plurality of combustion chambers formed in the engine, respectively. The method according to claim 1,
Wherein the first rotation section of the cam groove is provided such that the distance from the rotation axis of the swirl valve is changed along the longitudinal direction so that the insertion projection is pivoted while sliding on the first rotation section. The method of claim 3,
Wherein the first rotation section is formed in a curved shape such that the rotation angle of the intake valve caused by the sliding insertion protrusion is uniformly adjusted with respect to the rotation angle of the swirl valve. The method according to claim 1,
Wherein the cam groove is formed with a non-rotating section having a constant distance from the rotation axis of the swirl valve along the longitudinal direction so that the insertion projection slidable in at least a part of the section except the first rotation section is not rotated. The method of claim 5,
When the swirl valve is rotated in one direction from the reference state corresponding to the maximum open state of the intake valve, the cam groove of the cam plate is provided such that the insertion projection is positioned on the first rotation section,
Wherein a swirling groove is formed in the divided flow paths provided with a swirl valve therein such that the swirl valve is further rotatable in one direction from a set angle. The method of claim 6,
Wherein when the swirl valve is rotated from the reference state to the other direction, the cam groove of the cam plate is provided such that the insertion projection is positioned on the non-rotating section. The method of claim 7,
Wherein the first rotation section is provided in a curved shape such that the rotation angle of the intake valve caused by the sliding insertion protrusion has a constant ratio with respect to the rotation angle of the swirl valve. The method of claim 8,
A driving unit for providing rotational force to the swirl valve; And
And a control unit controlling the driving unit to adjust the rotation angle of the swirl valve,
Wherein the controller adjusts the swirl angle of the swirl valve so that the insertion projection slides in the first rotation section in the regeneration mode of the DPF apparatus provided on the exhaust flow path, / RTI > The method of claim 6,
The cam groove has a second rotation section in which at least a section of the cam groove except for the non-rotation section is rotated while the insertion projection is slid according to the rotation of the swirl valve, and a non-rotation section is formed between the first rotation section and the second rotation section Wherein the intake valve is arranged such that a section of the intake valve is located. The method of claim 10,
When the swirl valve is rotated from the reference state corresponding to the maximum open state of the intake valve to the other direction, the cam groove of the cam plate is provided such that the insertion projection is positioned on the non-rotating section or the second rotating section Intake regulator of a vehicle. The method of claim 11,
A driving unit for providing rotational force to the swirl valve; And
And a control unit controlling the driving unit to adjust the rotation angle of the swirl valve,
The control unit adjusts the rotation angle of the swirl valve so that the insertion protrusion slides in the second rotation section in the regeneration mode of the LNT apparatus provided on the exhaust passage, and in the regeneration mode of the DPF apparatus provided on the exhaust passage, Wherein the opening degree of the swirl valve is adjusted within the rotation groove section by adjusting the swirl angle of the swirl valve so as to be slid in the swirl groove section.

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