JPH03286132A - Air intake device for multiple cylinder engine - Google Patents

Abstract

PURPOSE:To strengthen the turning-over operation of air intake pressure waves at a volume chamber and obtain an excellent inertia effect, by arranging so that the outer peripheral portion of a rotary valve controlling connection between the volume chamber and each air intake passage by means of rotation, may be projected into the air intake passage at the time of valve closing. CONSTITUTION:A rotary valve 10 is provided within a volume chamber which is at the middle of an independent air intake passage 7, and the control of connection between the air intake passage 7 and the volume chamber is made by conducting the opening/closing rotation of this rotary valve 10. This valve 10 projects into the air intake passage 7 at the time of valve closing, so a crossing portion area with the air intake passage 7 under its valve opening condition becomes large, and its opening portion toward the air intake passage 7 can be made large, and the turning- over operation of air intake pressure waves at the volume chamber at the time of inertia synchronization can be strengthened. Also, under this structure, the effective area of the air intake passage becomes smaller at the same extent with that of the rotary valve 10 portion that projects into the air intake passage 7 at the time of valve closing, but the outer peripheral of the valve 10 is of a circular arc face, so the flow of air intake is smooth.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an intake system for an engine, and particularly to one that supercharges intake air by utilizing dynamic effects.

(Prior art) In recent years, in order to improve the output performance of automobile engines,
It is known to utilize the inertia effect and resonance effect of the intake air within the intake system to increase its filling efficiency.

In supercharging based on the inertia effect of intake air, when the engine is in a predetermined rotation range (synchronous rotation range), the intake negative pressure wave generated in the intake boat when the intake valve opens at the beginning of the intake stroke of each cylinder is used as an independent intake. Propagate at the speed of sound toward the upstream side in the passage,
This negative pressure wave is reversed into a positive pressure wave in a predetermined volume part (volume chamber), and this positive pressure wave is propagated downstream along the same path to reach the same intake port just before the intake valve closes. The positive pressure wave forces intake air into the combustion chamber, increasing its filling efficiency.

On the other hand, in supercharging using the resonance effect of intake air, multiple cylinders of the engine are divided into cylinders that are equally spaced on the intake stroke and grouped into multiple cylinder groups, and the independent intake passages of the multiple cylinders in each cylinder group are They are gathered into one collective intake passage (resonant intake passage) at the upstream end, and a pressure inversion section consisting of a volume part is provided at a predetermined position of this collective intake passage. By matching the phase of the basic intake pressure wave generated in the intake boats of each cylinder in the cylinder group and the reflected pressure wave reversed at the pressure inversion section in the synchronized rotation range of the engine, the pressure inversion section and each cylinder are The pressure waves of the intake air that propagate back and forth between the cylinders are caused to resonate in the collective intake passage, and due to this resonance, the pressure vibrations that occur individually in each cylinder generate a resonance pressure wave with a large amplitude. is forced into the combustion chamber of the cylinder to increase charging efficiency.

Conventionally, as such an intake device, Japanese Patent Application Laid-Open No. 62-121
As shown in Publication No. 828, the independent intake passages connected to each of a plurality of cylinders are connected to two volume chambers defined by partition walls in a surge tank, and the independent intake passages of one group of cylinders are The opening to the volume chamber is positioned closer to one end of the surge tank than the opening to the volume chamber of the independent intake passage of the other cylinder group, and both volume chambers are communicated by a communication passage at one end of the surge tank. Some engines have an on-off valve disposed at one end of the communication passage to change the inversion part of the intake pressure wave by opening and closing the on-off valve, thereby achieving a dynamic effect over a wide rotation range of the engine.

(Problem to be Solved by the Invention) By the way, instead of using the surge tank as described above, the intake passages that communicate with the intake ports of each cylinder are communicated with each other by a communication passage serving as an intake volume chamber, and this communication passage and the intake Effects similar to those described above can be obtained by controlling communication with the passage. In that case, it may be possible to arrange an on-off valve made of an intermediary at the connection between the communication passage and the intake passage, and use this on-off valve to control the communication between the communication passage and the intake passage. Since the on-off valve sometimes protrudes into the intake passage, it is unavoidable that the effective cross-sectional area of the intake passage becomes smaller due to this on-off valve. Moreover, since the flow of intake air is disturbed by the on-off valve, intake resistance increases, and an increase in torque cannot be expected. On the other hand, the communication passage may be connected to the intake passage through a branch passage, and an on-off valve may be provided in each branch passage, but when the on-off valve is closed, a so-called stepped portion is created by the branch passage in the intake passage. This stepped portion disrupts the flow of intake air, resulting in intake resistance.

The present invention has been made in view of the above points, and its purpose is to change the configuration of the on-off valve that controls communication between the intake passage and the volume chamber, so that when the on-off valve is opened, the air flow from the intake passage to the volume chamber is changed. The objective is to ensure a large opening area to strengthen the reversal effect of the intake pressure wave in the volume chamber, and to reduce intake resistance by making it difficult for intake air to be disturbed by the on-off valve when the valve is closed.

(Means for Solving the Problem) In order to achieve the above object, in the invention according to claim (1), a volume chamber which becomes an inversion part of the intake pressure wave at the time of inertial tuning is provided in the intake passage. A rotatable rotary valve is installed in the engine, and this valve controls communication between the intake passage and the volume chamber.

Specifically, in the present invention, a volume chamber for inertial supercharging is provided in the middle of an intake passage connected to each of a plurality of cylinders,
A rotary valve is disposed within the volume chamber and controls communication between the volume chamber and each intake passage through rotation, and the rotary valve is configured such that its outer peripheral portion protrudes into the intake passage when the rotary valve is closed. It is a feature.

In the invention according to claim (2), the plurality of cylinders are divided into a plurality of cylinder groups in which the intake strokes are arranged at equal intervals, and the collective intake passages of each cylinder group that communicate with the cylinders via independent intake passages are arranged. They communicate through a communication passage, and the communication between this communication passage and the collective air intake passage is controlled by a rotary valve.

That is, the present invention has a plurality of cylinders divided into a plurality of cylinder groups so that the intake strokes are equally spaced, and the independent intake passages of each cylinder group are aggregated to form a collective intake passage for each cylinder group. A rotary valve is provided which connects the collective intake passages to each other through a communication passage and controls the communication between the collective intake passages through the communication passage through rotation, and when the rotary valve is closed, the outer periphery of the rotary valve is connected to the independent intake passage. It is characterized by being configured to protrude inward.

(Can be made) With the above configuration, in the invention according to claim (1), a rotary valve is disposed in the volume chamber in the middle of the intake passage, and by rotating this valve to open and close, the intake passage and the volume chamber are connected. communication is controlled. Since this rotary valve protrudes into the intake passage when the valve is closed, the area of its intersection with the intake passage when the valve is open is large, making it possible to enlarge the opening to the intake passage. The inversion effect of the intake pressure wave in the volume chamber can be strengthened.

In addition, with this structure, although the effective area of the intake passage is reduced by the amount that the rotary valve protrudes into the intake passage when the valve is closed, the outer periphery of the rotary valve is an arcuate surface, so the intake air flows more smoothly than with a medium. Such peeling is less likely to occur, and therefore, the intake resistance does not increase significantly.

Further, in the invention according to claim (2), the collective intake passages between the cylinder groups are communicated with each other by a communication passage, and communication control between the communication passage and the collective intake passage is performed by a rotary valve, so that the rotary valve is opened. At the time of valve operation, the collective intake passages are communicated with each other through a communication passage, and this communication passage is used as a volume chamber to obtain a resonance effect. At this time, similarly to the above, the opening to the collective intake passage when the rotary valve is open becomes larger, and the reversal effect of the intake pressure wave in the communication passage increases. Further, when the valve is closed, intake air flows smoothly along the arcuate outer peripheral surface of the rotary valve, and intake resistance is small.

(Example) Embodiments of the present invention will be described below based on the drawings.

1 to 3 show a first embodiment of the present invention. Reference numeral 1 denotes an in-line four-cylinder engine, and the engine 1 includes a cylinder block 2, a cylinder head 3 assembled on the upper surface of the cylinder block 2, and a cylinder block 2. has. Above cylinder block 2
The first to fourth four cylinders C] to C4 are formed in series in the bank length direction, and these cylinders C1 to C4 are, for example,
The intake stroke progresses in the order of first cylinder C1 - third cylinder C3 - fourth cylinder C4 - second cylinder C2.

Each cylinder C1 to C4 is provided on the left side of the cylinder head 3.
Intake ports 6 communicating through the intake valves 5 are opened, and each intake port 6 is connected to a downstream end of an independent intake passage 7 having a circular cross section. Each independent intake passage 7 is curved upward and connected to a surge tank 8.

A collective intake passage 9 is connected to one end of the cylinder row of the surge tank 8, and the collective intake passage 9 is connected to a throttle body (not shown).

A rotary valve 10 is disposed inside the upwardly curved portion of each independent intake passage 7 and extends parallel to the cylinder row. This rotary valve 10 has a cylindrical casing 11 that is integrally formed with the intake pipe 7a of the independent intake passage 7 and extends parallel to the cylinder row to the position of the independent intake passage 7.7 at the front and rear ends. 11 communicates with each of the independent intake passages 7 through communication holes 12 that open at positions of equal length from the intake port 6.

Further, as shown in FIG. 3, a closed cylindrical valve body 13 supported by a support shaft 15 is rotatably fitted into the casing 11, and a communication passage 17 is formed within the valve body 13. There is. A plurality of valve holes 14, 14, . It is arranged at a position corresponding to each of the communication holes 12 described above. A lever 16 is attached to the support shaft 15, and this lever 16 is connected to an actuator (not shown).By rotating the valve body 13 with the actuator, each valve hole 14 is connected to the corresponding communication hole 12. The rotary valves 1o are opened by aligning the four independent intake passages 7, 7 . . . . are simultaneously communicated with each other via the communication passage 17 in the valve body unit 3, and the volume chamber that becomes the inversion part of the intake pressure wave during inertial tuning in the cylinders C1 to C4 is connected to the surge tank 8 or the communication passage 17. It is now possible to switch to .

When the rotary valve 10 is closed, the outer peripheral portion of the valve body 13 partially protrudes into the independent intake passage 7, as shown in FIG.

In FIG. 1, 31 is an exhaust boat that is opened and closed by an exhaust valve 32, and 33 is an injector.

Therefore, in this embodiment, in the low speed rotation range of the engine 1, the rotary valve 10 is in a closed state, and inertial tuning is achieved in which the pressure waves of the intake air generated at the intake ports 6 of the cylinders C1 to C4 are reversed at the surge tank 8. arise.

At that time, the valve body 13 of the rotary valve 10 in the closed state
protrudes into the independent intake passage 7, there is no need to connect the communication passage with a branch passage as in the conventional case, and the intake air is not disturbed by the stepped portion.

Further, the effective cross-sectional area of the independent intake passage 7 is reduced due to the protrusion of the valve body 13 into the independent intake passage 7, but since the protruding portion of the valve body 13 is an arcuate surface, the intake air in the independent intake passage 7 is The air flows smoothly along the air, and no separation occurs, thereby avoiding an increase in intake resistance.

On the other hand, in the high speed range of engine 1, rotary valve 1
0 valve body 13 rotates around the support shaft 18, and its respective valve holes 1
4 coincide with the corresponding communication holes 12 of the casing 11, the rotary valve 10 becomes open, and each cylinder C
1 to C4R independent intake passages 7, 7. ...They are the communication hole 12, the valve hole 14 of the valve body 13, and the communication passage 17 in the valve body 13.
communicate with each other via. In this state, cylinders C1 to C
The pressure wave of the intake air generated at the intake port 6 of No. 4 is reversed in the communication passage 17, and the inertia-tuned rotation speed shifts to the high speed rotation range of the engine 1.

At this time, since the valve body 13 of the rotary valve 10 has a structure that protrudes into the independent intake passage 7, the area of the intersection of the valve body 13 with the independent intake passage 7 inevitably becomes large, and the area of the valve hole 14 of the valve body 13 inevitably becomes large. A large opening is ensured. Therefore, the pressure wave of the intake air during the inertial tuning is reliably propagated to the communication passage 17 in the valve body 13 and reversed, so that a good inertial effect can be reliably obtained.

Incidentally, as shown in FIG. 4, the rotary valve 10 may be arranged outside the curved portion of the independent intake passage 7.

In this case, the valve hole 14 of the valve body 13 of the rotary valve 10 disposed on the outside of the independent intake passage 7 in the curving direction The inertia effect can be further increased.

FIG. 5 shows the second embodiment. In each of the following embodiments,
The same parts as those in the figures of the first embodiment are given the same reference numerals, and detailed explanations thereof are omitted), and the communication passage 17 is provided separately rather than within the valve body 13 of the rotary valve 10. In this embodiment, a communication passage 17 extending in the cylinder row direction is provided outside the curved portion of the independent intake passage 7, and this communication passage 17 communicates with the independent intake passage 7 via branch passages 18, respectively. The branch passage 18 is provided with a rotary valve 10' that opens and closes the branch passage 18 to control communication between the communication passage 17 and the independent intake passage 7. This rotary valve 10' is different from that of the above embodiment in that a valve hole 14' for opening and closing the branch passage 18 is formed through the valve hole 14' in the diametrical direction. The valve is now open. In this embodiment as well, the same effects as in the above embodiment can be obtained.

6 and 7 show a third embodiment. In this embodiment, the outer peripheral portion of the valve body 13' of the rotary valve 10, which protrudes into the independent intake passage 7 when the valve is closed, is arranged along the independent intake passage 7. A notch 13a' is formed in the. In this embodiment, since the notch 13a' on the outer periphery of the valve body 13' is shaped along the independent intake passage 7, when the valve is closed, the valve body 13'
Since there is no longer a portion projecting into the independent intake passage 7, intake resistance can be further reduced.

Incidentally, as shown in FIG. 8, the same effect can be obtained even if the independent intake passage '7 has an elliptical cross section.

FIG. 9 shows a fourth embodiment, which is applied to a type 6 six-cylinder engine 1'. That is, in this embodiment, in a V-type six-cylinder engine 1' having front and rear banks BF and BR, the cylinder block 2 of the front bank BF (the one on the left side in the figure) has the first, third, and fifth odd-numbered cylinder blocks. There are six numbered cylinders cl, C3 and C5, and the second, fourth and sixth even numbered six cylinders C2, C4 and C6 are in the cylinder block 2 of the rear bank BR (the one on the right in the figure). The cylinders C] to C6 are formed in series in the bank length direction (direction perpendicular to the plane of the drawing), and the intake strokes of the cylinders C] to C6 proceed in the order of cylinder numbers, for example.

In this embodiment, the six cylinders C1 to C6 are divided into two groups of front and rear cylinders for each bank of three cylinders, BF and BR, so that the intake strokes are equally spaced from each other.

In each cylinder head 3, an intake port 6 is opened on the side surface between the banks BFBR, and the three independent intake passages 7, 7°, for each bank BF, BR each go upward and then curve backward. It extends above the cylinder head 3 of the rear bank BR, and is connected to a surge tank 8E8R corresponding to each bank BF, BR. Then, the outside (front side) of the curved portion of each independent intake passage 7 of the front bank BF and the inside (rear side) of the curved portion of each independent intake passage 7 of the rear bank BR.
A rotary valve 10.10 is disposed at each of the rotary valves 10.10.

Therefore, in this embodiment, both rotary valves 10, 10 are opened and closed synchronously depending on the rotational range of the engine 1', and the inertia-tuned rotational speeds of the cylinder groups of banks BF and BR are switched. This embodiment also provides the same effects as those of the above embodiment.

In addition, as shown by virtual lines in the figure, both rotary valves 10
．． 10 may be changed to the inside (rear side) of the curve of each independent intake passage 7 of the front bank BF and the outside (front side) of the curve of each independent intake passage 7 of the rear bank BR. In addition, as shown in Fig. 10, both rotary valves 10.10
may be arranged inside the curved part (rear side) of the independent intake passage 7 of each bank BF, BR, or furthermore, as shown in FIG. It's okay. Similar effects can be obtained in these cases as well.

12 and 13 show the fifth embodiment, in which both banks B
The F and BR rotary valves are shared. In this embodiment, as shown in FIG. 12, in the same configuration as the second embodiment, the inside curved portion (rear side) of each independent intake passage 7 of the front bank BF and each independent intake passage 7 of the rear bank BR are used. One rotary valve 10 on the outside (front side) of the curved part of
or has been set up. This rotary valve 10 includes independent intake passages 7, 7 . Three pairs of communication holes 12, 12 . ... are formed by making six pairs of them face each other in a substantially diametrical direction. Further, as shown in FIG. 13, the cylindrical valve body 13 is opened with three pairs of valve holes 1414, which coincide with the communication holes 12, respectively, and the communication passages 17 of the valve body 13 are opened. , each bank BF, B
R independent intake passage 7.7. ...each other and bank BF
, BR between the independent intake passages 7, 7. ... are made to communicate with each other through a communication path 17.

Therefore, in this embodiment, the rotary valve 10 can be shared between the banks BF and BR, which has the advantage of simplifying the structure.

FIG. 14 shows a sixth embodiment, and in the configuration of the embodiment shown in FIG. 11, an independent intake passage 7 between both banks BF and BR
,7. ...I try to communicate with each other. That is, in this embodiment, the casings 1111 of both rotary valves 1010 are communicated with each other through the communication passage 19 at one end of each. In addition, each valve hole 1 is provided in the valve body 13.
4 is formed with an opening 20 that communicates with the communication passage 19 when the banks BF and BR communicate with the communication hole 12 of the casing 11. At the same time, the independent intake passages 77, . . . between the banks BF and BR are communicated through the passage 17.
9 to communicate with each other. Similar effects can be obtained in this embodiment as well.

FIGS. 15 and 16 show a seventh embodiment, in which a rotary valve 10 is used to switch the resonance effect. That is, similarly to the fourth embodiment, in the V-type six-cylinder engine 1', the six cylinders C1 to C6 are divided into two cylinder groups for each bank BF and BR so that the intake strokes are equally spaced. Independent intake passages 7, 7 for each cylinder group. ...
are gathered together and connected to the collective intake passages 9, 9 for each cylinder group, and the recollected intake passages 9.9 are gathered together at the upstream end. A cylindrical rotary valve 10 for controlling communication between the regathering intake passages 9.9 is disposed in the middle of the regathering intake passages 9.9.

Therefore, in this embodiment, by switching the rotary valve 10 open/close, the common intake passage 9 between the cylinder groups,
9 changes, and in the low speed rotation range of the engine 1', the rotary valve 10 closes and the intake passages 9, 9 are reunited.
9 communicates at the upstream end gathering part. Therefore, resonance tuning occurs between the cylinder groups, with this upstream end gathering portion serving as a reversal portion of the intake pressure wave.

In this case, similarly to the first embodiment, the valve body 13 of the rotary valve 10 in the closed state protrudes into the collective intake passage 9,
Although the effective cross-sectional area of the collective intake passage 9 is reduced, this valve body 1
Since the protruding portion 3 is an arcuate surface, the intake air in the collective intake passage 9 flows smoothly along the arcuate surface, and its intake resistance does not increase.

On the other hand, in the high-speed rotation range of the engine 1', the rotary valve 10 opens and the recollected intake passages 9, 9 also communicate with the communication passage 17 in the valve body 13 of the rotary valve 10. This causes resonance tuning in which the communication passage 17 serves as an inversion part of the intake pressure wave, and the resonance tuning rotation speed is switched to a high speed rotation range.

At this time, the area of the intersection of the valve body 13 of the rotary valve 10 with the collective intake passage 9 is increased, and the opening of the valve hole 14 is ensured to be large. Therefore, the pressure wave of the intake air during the resonance tuning is reliably propagated to the communication passage 17 in the valve body 13 and reversed, so that a good resonance effect can be reliably obtained.

(Effect of the invention) As explained above, according to the invention claimed in claim (1),
A volume chamber for inertial effect is provided in the middle of the intake passage connected to each cylinder of the engine, and communication control between this volume chamber and the intake passage is controlled by a rotary valve.When the rotary valve opens, the volume increases. By increasing the opening area of the chamber to the intake passage, the reversal effect of the intake pressure wave in the volume chamber can be strengthened, and a good inertia effect can be obtained.At the same time, when the valve is closed, the intake air flows smoothly through the intake passage and the intake air is increased. Resistance can be reduced.

Further, according to the invention according to claim (2), in a multi-cylinder engine that is divided into a plurality of cylinder groups in which the intake strokes are arranged at equal intervals, the collective intake passages of each cylinder group are connected to each other. By providing a passage and using a rotary valve to control the communication between the collective intake passages through this communication passage, the same effect as above can be obtained without using the communication passage as an inversion part of the intake pressure wave during resonance tuning. be able to.

[Brief explanation of drawings]

1 to 4 show a first embodiment of the present invention, FIG. 1 is a sectional view of the engine and intake system, FIG. 2 is a schematic plan view of the same,
FIG. 3 is a schematic perspective view of the rotary valve, and FIG. 4 is a view corresponding to FIG. 1 showing a modification of the arrangement structure of the rotary valve. FIG. 5 is a diagram corresponding to FIG. 1 showing the second embodiment. 6th
Figures to Figures 8 show the third embodiment, Figure 6 is a view equivalent to Figure 1, Figure 7 is a sectional view taken along the line ■-■ of Figure 6, and Figure 8 is equivalent to Figure 7 showing a modification. It is a diagram. Figures 9 to 11 show the fourth embodiment; Figure 9 is a diagram equivalent to Figure 1; Figures 10 and 11 are equivalent to Figure 1;
Each figure is a view corresponding to FIG. 1 showing a modification of the arrangement structure of the rotary valve. 12 and 13 show the fifth embodiment, in which FIG. 12 is a diagram equivalent to FIG. 1, and FIG. 13 is a diagram equivalent to FIG. 3. FIG. 14 is a diagram corresponding to FIG. 3 showing the sixth embodiment. 15 and 16 show a seventh embodiment, FIG. 15 is a schematic plan view of the engine and intake system, and FIG. 16 is a sectional view taken along the line XVI-XVI in FIG. 15. 1.1'...Engine C1 to C12...Cylinder 6...Intake port 7...Independent intake passage 9...Common intake passage 10.10'...Rotary valve 17...Communication passage 7th ward, 8th ward

Claims (2)

[Claims] (1) A volume chamber for inertial supercharging is provided in the middle of each intake passage connected to a plurality of cylinders, and a rotary valve is installed in the volume chamber to control communication between the volume chamber and each intake passage through rotation. 1. An intake system for a multi-cylinder engine, wherein the rotary valve is configured such that an outer circumferential portion thereof protrudes into an intake passage when the rotary valve is closed. (2) It has a plurality of cylinders divided into a plurality of cylinder groups so that the intake strokes are equally spaced, and the independent intake passages of each cylinder group are collected and connected to a collective intake passage for each cylinder group. The collective intake passages between the cylinder groups are communicated with each other by a communication passage, and a rotary valve is provided which controls communication between the collective intake passages through the communication passage through rotation, and when the rotary valve is closed, the outer peripheral portion thereof is connected to the collective intake passage. An intake device for a multi-cylinder engine, characterized in that it is configured to protrude into a passage.