JPH0842347A - Intake device of multi-cylinder engine - Google Patents

Abstract

PURPOSE:To miniaturize an intake system for exhibiting the intake dynamic effect and also to make it have high rigidity in an intake device of a multi- cylinder engine wherein respective independent intake passages corresponding to respective cylinders are communicated with one another by a volume chamber through branch passages branched from the way of respective independent intake passages, and the dynamic effect of intake air is exhibited in the wide operating range by opening and closing the branch passages by a control valve. CONSTITUTION:Besides a first volume chamber 8a to which an independent intake passage 6 facing respective cylinders is connected, a second volume chamber 8b for communicating respective independent intake passages 6 with one another through a branch passage 13 branched from the way of the independent intake passage is provided, and a control valve 14 for opening and closing respective branch passages 13 according to the operating state of an engine is provided. Passage walls of respective independent intake passages 6 constitute a part of a constitution wall of the second volume chamber 8b.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of an intake system for a multi-cylinder engine that utilizes the dynamic effect of intake air to improve output.

[0002]

2. Description of the Related Art Conventionally, in an intake system of an engine, a negative pressure wave (a pressure wave of negative pressure) generated with the start of intake is reflected and inverted at the open end to the atmosphere on the upstream side of the intake passage or the intake expansion chamber to be positive. Utilizing the fact that a pressure wave (pressure wave of positive pressure) is returned to the intake port direction, the positive pressure wave reaches the intake port just before the intake valve is closed and pushes the intake air into the combustion chamber. It is known to increase the charging efficiency of the intake air by the inertia effect of. When such a technique is used, if the shape of the intake passage is constant, the vibration cycle of the pressure wave generated in the intake passage and the opening / closing cycle of the intake valve are matched to enhance the intake inertia effect. Limited to specific rotation range.

Therefore, in the past, Japanese Patent Laid-Open No. 56-11581
As disclosed in Japanese Patent Publication No. 9, the length of the intake passage is changed according to the number of revolutions of the engine. For example, the intake passage for each cylinder is bifurcated in the upstream portion to form a long passage and a short passage. And the upstream ends of these passages are opened to the intake expansion chamber and the like, and a control valve is provided in a short passage so that the effective length of the intake passage is shortened by opening this control valve in the high rotation range. (See FIG. 6 of the above publication) is proposed, and according to the intake system of the engine, the inertial effect of intake can be enhanced in the low rotation range and the high rotation range.

[0004]

However, in the above-mentioned conventional structure, the independent intake passage corresponding to each cylinder is simply communicated with the volume chamber through the branch passage branched upward from the independent intake passage. Since the intake system is not too rigid, not only is the rigidity of the intake system insufficient, but the intake system becomes large in size, which poses a problem when mounted on a vehicle.

The present invention has been made in view of the above points, and is intended to improve the output by the intake dynamic effect over a wide operating range, and to reduce the size of the intake system that exhibits the intake dynamic effect. The challenge is to achieve high rigidity.

[0006]

In order to solve the above-mentioned problems, the means of the invention of claim 1 is a multi-cylinder in which an independent intake passage is provided downstream of the first volume chamber corresponding to each cylinder. In an intake device of an engine, a branch passage that is branched from the middle of each of the independent intake passages, and is connected to the other end of each of the branch passages, and communicates between the independent intake passages through the respective branch passages. A second volume chamber, and a control valve provided in each of the branch passages, the control valve being opened / closed so as to open / close the branch passage according to the operating state of the engine, and the passage wall of the independent intake passage is the second volume chamber. It is assumed that it constitutes a part of the wall that constitutes.

As a result, in the first aspect, the control valve is opened / closed according to the operating state of the engine. Then, when the control valve is closed, each cylinder communicates with the first volume chamber through the corresponding independent intake passage, while when the control valve is opened, each cylinder is connected from the corresponding independent intake passage and the middle thereof. Since it also communicates with the second volume chamber via the branched branch passage, the dynamic effect of intake air is exhibited over a wide operating range, and the output is improved.

In this case, the passage wall of the independent intake passage constitutes a part of the constituent wall of the second volume chamber, and the intake system parts exhibiting the above-mentioned intake dynamic effect are effectively utilized and commonly used. Therefore, the intake system can be made compact, and a part of the constituent wall of the second volume chamber is not required, so that the weight can be reduced accordingly. Further, as a result, the passage walls of the independent intake passages and some of the constituent walls of the second volume chamber are combined, so that the independent intake passages are connected to each other by the constituent wall of the second volume chamber. Also, the rigidity of the intake system can be improved.

According to the second aspect of the present invention, the control valve is opened / closed according to the engine speed as an engine operating state, the branch passage is closed in the low engine speed region and the branch passage is opened in the high engine speed region. I am trying. This allows
While the output is improved by the intake dynamic effect in the low rotation range and the high rotation range, the intake system can be made compact, lightweight and highly rigid as in the first aspect.

Further, in the invention of claim 3, the control valve in claim 2 is opened and closed only in a region where the engine load is equal to or higher than a predetermined load. As a result, the opening and closing of the control valve is performed only in the high load region of a predetermined load or more, so that the frequency of opening and closing the control valve can be minimized and the reliability of the control valve can be improved.

[0011]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will now be described in detail with reference to the drawings.

1 to 4 show an embodiment in which the present invention is applied to a 4-cylinder 4-cycle engine. In the figure, reference numeral 1 denotes an engine body composed of a cylinder block 2 and a cylinder head 3 and the like, and the first to fourth four cylinders 4, 4, ... Are formed in series in the longitudinal direction of the engine body 1. Has been done. A combustion chamber 5 is formed in each of the cylinders 4.

Reference numeral 6 denotes an independent intake passage provided independently of each other for each cylinder, and each of the independent intake passages 6 is formed in the cylinder head 3 and constitutes an intake port forming a downstream end portion of the independent intake passage 6. It opens to the combustion chamber 5 of each cylinder 4 via 7. The reference numeral 8 designates an intake expansion chamber composed of a substantially rectangular tubular tank extending parallel to the longitudinal direction of the engine. The intake expansion chamber 8 is vertically partitioned by a partition plate 9 and has a relatively large volume on the upper side. It is divided into a volume chamber 8a and a second volume chamber 8b having a relatively small volume on the lower side. The upstream ends of the independent intake passages 6, 6 ... Are connected to the first volume chamber 8a of the intake expansion chamber 8 with substantially the same passage length. An intake air introducing pipe 10 for introducing outside air is connected to one end surface of the first volume chamber 8a, and a throttle valve 11 for controlling an intake air amount is provided in the intake air introducing pipe 10.
The intake air introduced into the first volume chamber 8a by the intake introduction pipe 10 is supplied to the combustion chamber 5 of each cylinder 4 through each independent intake passage 6. An intake valve 12 is provided in the intake port 7.

Further, a second passage 13 as a branch passage is branched from an intermediate point of each of the independent intake passages 6, and the other ends of the respective second passages 13, 13 ... Have substantially the same passage length. The intake expansion chamber 8 is connected to the second volume chamber 8b so that the independent intake passages 6, 6 ... Are in communication with each other by the second volume chamber 8b and each second passage 13. The volume chamber 8b and the second passage 13 form a communication passage that connects the independent intake passages 6, 6 ... In this case, as shown in FIG. 1, the second passage 13 joins the independent intake passage 6 at an acute intersection angle.

A butterfly type shutter valve 14 as a control valve for opening and closing the second passage 13 is provided near the opening of each second passage 13.
Each shutter valve 14 is rotatably supported by a valve shaft 15 extending parallel to the longitudinal direction of the intake expansion chamber 8. In this case, as shown by the alternate long and short dash line in FIG. 1, one end of the shutter valve 14 advances into the independent intake passage 6 while the other end of the shutter valve 14 retreats into the second passage 13 and Are provided so as to be located on the downstream side of the rotation axis of the shutter valve 14 in the intake air inflow direction. Since the shutter valve 14 is provided in this way, intake air flowing through the independent intake passage 6 flows downstream along the surface of the butterfly shutter valve 14 on the independent intake passage side, so that one end of the shutter valve 14 is opened when the valve is opened. Despite advancing into the independent intake passage 6, the increase in intake resistance can be suppressed as much as possible.

Although not shown, each shutter valve 14 is controlled to be opened / closed via an actuator by a control circuit that receives an output of engine speed detecting means or the like, and each independent intake passage 6 formed by the second volume chamber 8b. , 6 ... Controls communication between each other according to the engine operating state, and is controlled so as to be closed in a low speed range where the engine speed is less than a set value and opened in a high speed range where the engine speed is higher than the set value. It It should be noted that the opening / closing operation of the shutter valve 14 according to the engine speed as described above may be performed at least during high load when output is required, and when the load is low, the shutter valve 14 is opened or closed. It may be kept.

In such an intake system, 16 is the intake expansion chamber 8 and each of the independent intake passages 6 and 6.
, And each of the second passages 13, 13 ..., which is an intake system structure, and the structure 16 is a tank that constitutes the intake expansion chamber 8 (first volume chamber 8a and second volume chamber 8b). The part 17 and a part of the constituent wall, that is, the side wall and the lower wall, which extend around the periphery of the tank part 17 from the upper side of the side opposite to the engine side of the tank part 17 to the side and the lower side. The integral intake pipe integrally forming the upstream side portions 6a, 6a ... Of the independent intake passages 6, 6 ... so that the upstream ends thereof open to the upper side of the side of the tank portion 17 (first volume chamber 8a). .. and the respective integral intake pipe portions 18, 1
8 ... Branches from the lower side toward the engine side for each cylinder, and extends downstream from the independent intake passages 6, 6 ...
6b, and the lower wall of the constituent walls of the tank portion 17 (second volume chamber 8b) in the vicinity of the branch intake pipe portion 19 of each of the integral intake pipe portions 18 described above. Then, the communication pipe portions 20, 2 integrally forming the second passage 13 communicating with the second volume chamber 8b in the middle of each independent intake passage 6
0 and a flange portion 21 that connects the tip portions of the branch intake pipe portions 19, 19 to each other, and the flange portion 21 connects the branch intake pipe portion 19 to the engine body 1 downstream of the independent intake passage. The side portions 6b are fixed to the engine body 1 by inserting and tightening the bolts 22 from the side while the side portions 6b are fitted to the intake ports 7 of the cylinders 4.
The upper part of the side of the tank portion 17 on the engine side is formed so as to bulge toward the engine side.
The volume of a is secured sufficiently. Also, FIG.
As shown in FIG. 3 and FIG. 3, the downstream side portion 6b of each independent intake passage 6 is integrally connected by the constituent wall forming the second volume chamber 8b, and the downstream side portion 6b of each independent intake passage 6b.
Of the second volume chamber 8b constitutes a part of the wall of the second volume chamber 8b.

Further, the independent intake passage downstream side portion 6b of each branch intake pipe portion 19 and each intake port 7 extend in a substantially straight line from diagonally above toward the combustion chamber 5 and open into the combustion chamber 5. Has been formed. An injection valve mounting hole 23 is formed in the upper portion of the branch intake pipe portion 19 near the downstream end of the independent intake passage downstream side portion 6b.
4 has its tip injection port portion inserted and fixed in the mounting hole 23 via a seal ring 23a. This mounting hole 23
The fuel injection valve 24 is mounted so that the fuel from the injection valve 24 is injected toward the intake valve 12 of the combustion chamber 5, and the fuel injection valves 24, 24 ... Are arranged in the longitudinal direction of the engine. The fuel supply pipes 25 arranged in parallel are communicatively connected. As a result, the fuel injection valve 24 is mounted in a lying state substantially along the branch intake pipe portion 19, and the intake expansion chamber 8 (tank portion 17 is provided on the extension line 1 of the center line of the fuel injection valve 24). ) Is located close to the fuel injection valve 24 and the fuel supply pipe 25.

Further, the second passage 13 of each of the communication pipe portions 20 described above.
Is provided with the shutter valve 14, and the intake expansion chamber 8 (tank portion 17) is provided with a center extension line l of the fuel injection valve 24.
Since it is located above, the intake system structure 16 has the intake expansion chamber 8 in the tank portion 17 at a position lower than the center extension line 1 and including the second passages 13, 13.
Of the second volume chamber 8b and the first volume chamber 8 of the intake expansion chamber 8
It is formed by dividing the upper and lower parts of the tank part 17 and each integral intake pipe part 18 at a position of the partition plate 9 between a and a by a dividing surface along the longitudinal direction of the intake expansion chamber 8. , 18 ... Upper half 1 integrally formed with the upper half part
6a, the lower half of the tank portion 17, the integrated intake pipe portions 18, 1
8 is composed of a lower half part, branch intake pipe parts 19, 19 ..., communication pipe parts 20, 20 ... and a lower part 16b integrally formed with a flange part 21, and both parts 16a, 16b.
Are joined via the partition plate 9, and the bolts 26, 26 ...
Are tightly connected by inserting from below and tightening.

Further, as shown in detail in FIG. 4, each second passage 13 is formed in the lower wall of the tank portion 17 (second volume chamber 8b).
Are integrally formed between the openings to the second volume chamber 8b and at both ends thereof so as to rotatably support the valve shaft 15 of the shutter valve 14, and the periphery of each of the openings, that is, the shutter. Rib portions 28, 28 ... Which are annularly raised so as to continuously connect the boss portions 27, 27 are integrally formed on the valve seat portion on which the valve body 14a of the valve 14 is seated. Intake expansion chamber 8 is formed by bosses 27, 27 ...
The rigidity of the (tank part 17) in the longitudinal direction of the engine is increased.

Further, as shown in FIG. 4, the second passage 13 is drilled from the second volume chamber 8b side by a drill, and the connection portion of the second passage 13 with the independent intake passage is smoothed.
Formed in the second portion 13 to suppress the change of the passage cross-sectional area of the second passage 13 to be small and gentle, and to prevent the flow resistance from the second volume chamber 8b to the independent intake passage 6 via the second passage 13 and its change. Is kept small. Further, 29 is a rib portion which is formed along the boss portion 27 and which connects the annular rib portions 28, 28 around the opening of the second passage 13 to each other.

Next, the operation of the above embodiment will be described. When the shutter valves 14 are closed and the second passage 13 is closed, the communication between the independent intake passages 6, 6 ... By the second volume chamber 8b is cut off. In this state, the negative pressure wave generated in the intake stroke of each cylinder 4 propagates to the first volume chamber 8a and is reflected there, that is, the negative pressure wave and its reflected wave propagate through a relatively long passage, so that the low pressure wave is reduced. The vibration cycle of such a pressure wave matches the intake valve opening / closing cycle in the rotation range, the inertia effect of intake air in the low rotation range is enhanced, and the intake charging efficiency is enhanced.

On the other hand, in a state where the shutter valves 14 are opened, the second passage 13 is opened, and the independent intake passages 6, 6 ... Are communicated with each other by the second volume chamber 8b, The negative pressure wave generated in the intake stroke is reflected by the second volume chamber 8b through the second passage 13 and the passage length used for propagating the negative pressure wave and the reflected wave is shortened. The inertial effect is enhanced, and the pressure wave propagating from other cylinders in this operating range also receives the second volume chamber 8b.
Thus, the filling efficiency in the high rotation range is significantly improved. Therefore, at least when the load is high, at a predetermined rotational speed corresponding to an intermediate rotational speed of each rotational speed at which the intake inertia effect of the low rotational speed and the high rotational speed is obtained,
By closing the shutter valve 14 on the lower rotation side and opening the shutter valve 14 on the higher rotation side than this, the intake charging efficiency can be increased and the output can be improved in the entire rotation range. In particular, the intake charge efficiency in the high engine speed range is further enhanced by the pressure propagation action between the cylinders, as compared with the conventional case where the intake passage is simply shortened to increase the inertia effect. .

Further, when the intake stroke ends and the intake valve 12 closes the intake port of the combustion chamber 5, the pressure wave is transmitted to the intake port 7 of the independent intake passage 6 by the propagation of the reflected wave, but the pressure wave is intaken. After being reflected by the valve 12, the second passage 1
3 and the second volume chamber 8b to be propagated and introduced into the independent intake passage 6 in the intake stroke. In this case, since the second passage 13 merges with the independent intake passage 6 with an acute angle of intersection, the pressure wave is transmitted from the independent intake passage 6 after the intake stroke to the middle of the independent intake passage 6. After being smoothly introduced into the second passage 13 that opens in the section, the second volume chamber 8b and the second passage 13 that opens in the middle of the independent intake passage 6 in the intake stroke smoothly into the independent intake passage 6 in the intake stroke. be introduced. Therefore, the pressure wave is efficiently transmitted to the intake port 7 of the independent intake passage 6, so that the intake charging efficiency is improved.

The sizes of the first and second volume chambers 8a and 8b suitable for effectively exhibiting the above-mentioned action are as follows: the first volume chamber 8a has a capacity of 0.5 times the displacement or more. It is desirable that the volume of the second volume chamber 8b be 1.5 times or less the displacement. Further, the second volume chamber 8b
It is desirable to make the volume smaller than that of the first volume chamber 8a, and make the cross-sectional area of the second volume chamber 8b larger than the cross-sectional area of each independent intake passage 6.

In this case, the intake expansion chamber 8 (the first volume chamber 8a and the second volume chamber 8b in the intake system structure 16).
), An integral intake pipe portion 18 that constitutes the upstream portion 6a of each independent intake passage 6, a branch intake pipe portion 19 that constitutes the downstream portion 6b of each independent intake passage 6, and each second passage. 13 and the communication pipe portion 20 constituting each unit 13, the individual intake passages 6 bypass the periphery of the intake expansion chamber 8 and are integrally formed by utilizing a part of the constituent wall of the intake expansion chamber 8 (tank portion 17). Since the second passages 13 are formed integrally with a part of the constituent wall of the intake expansion chamber 8 (second volume chamber 8b), the required length of the independent intake passage 6 and the intake air are increased. The first and second volume chambers 8a, 8 of the expansion chamber 8
In obtaining each required volume of b, these intake systems can be made compact and small, so that the required length and required volume can be sufficiently secured in a limited space (engine room). Therefore, the vehicle mountability can be improved.

Further, in this case, the passage wall of the downstream side portion 6b of each of the independent intake passages 6 constitutes a part of the constituent wall of the second volume chamber 8b, and the intake system which exhibits the intake dynamic effect is produced. Since the parts are effectively utilized and shared, the intake system can be made compact and the second volume chamber 8
Since part of the constituent wall of b is unnecessary, the weight can be reduced accordingly. In addition, as a result, the independent intake passage downstream portion 6
By making the passage wall of b and a part of the constituent wall of the second volume chamber 8b double, the downstream side portions 6b, 6 of the independent intake passages 6, 6 ...
b ... The two are connected by the constituent wall of the second volume chamber 8b, so that the rigidity of the intake system can be improved.

Further, in this case, the fuel injection valve 24 is close to the downstream end of the branch intake pipe portion 19, that is, the downstream side of the independent intake passage 6, and the injected fuel is atomized with good responsiveness to the combustion chamber 5. The tank portion 17 (the intake expansion chamber 8) of the intake system structure 16 is located close to the center extension line 1 of the fuel injection valve 24 because it is mounted toward the combustion chamber 5 to be supplied. , And it is necessary to dispose the shutter valve 14 in each of the second passages 13. Therefore, the intake system structure 16 in the tank portion 17 is located below the center extension line 1, that is, on the side of the branch intake pipe portion 19 and at the position of the partition plate 9 along the longitudinal direction of the intake expansion chamber 8. Upper divided body 16a and lower divided body 1 vertically
6b and the two divided bodies 16a, 16b are joined together via the partition plate 9, so that the lower divided body 16b is attached to the engine body 1 by the flange portion 21 of the bolt 2 from the side.
After mounting by tightening with 2, the lower divided body 16
Each fuel injection valve 24 is attached by inserting the fuel injection valve 24 into the injection valve mounting hole 23 of each branch intake pipe portion 19 of b from the direction of the center extension line 1 and fixing the fuel supply pipe 25 to the lower split body 16b. At the same time, the shutter valve 14 is inserted into the second passage 13 of each communication pipe portion 20 of the lower divided body 16b from above.
Is fixed to the valve shaft 15, and then the upper divided body 16a is joined to the lower divided body 16b with the partition plate 9 interposed therebetween, and the bolts 26 are tightened from below so that both 16a and 16b are joined together. By integrally connecting the shutter valve 14 and the fuel injection valve 24, it is possible to secure good moldability and easily assemble the upper and lower split bodies 16a and 16b. Can be performed easily, and good assembling property can be secured.

Moreover, since the upper divided body 16a and the lower divided body 16b are coupled by tightening the bolts 26 from below, the tank portion 17 is secured as described above while ensuring good assembling. There is also an advantage that a bulge can be formed in the upper portion of the side of the (intake expansion chamber 8) on the engine side, and a sufficient volume of the intake expansion chamber 8, especially the first volume chamber 8a, can be secured. The second volume chamber 8b is arranged in parallel with the first volume chamber 8a by vertically dividing the tank portion 17 of the intake system structure 16 by the partition plate 9, and a part of the wall of the first volume chamber 8a. Since the (partition plate 9) is formed in common, the intake system can be made more compact.

Further, the tank portion 17 (second volume chamber 8)
The lower wall of b) is integrally formed with boss portions 27, 27 ... Which rotatably support a valve shaft 15 extending in parallel to the longitudinal direction of the engine to which the valve body 14a of each shutter valve 14 is fixed. The bosses 27, 27 ... Are annular ribs 2 integrally formed around the opening of each second passage 13.
.. are connected in series, the rigidity of the intake expansion chamber 8 (tank portion 17) in the longitudinal direction of the engine is increased. Therefore, the vibrational deformation of the tank portion 17 due to the engine vibration is suppressed as much as possible, and the smooth opening / closing operation is stably ensured without interfering with the opening / closing of the shutter valve 14 as in the conventional case. Therefore, it is possible to ensure the above-mentioned intake inertia effect. Further, by integrally forming the boss portion 27 and the rib portion 28 on the constituent wall of the tank portion 17, the structure can be made compact and simplified.

It is needless to say that the present invention is not limited to the four-cylinder engine as in the above embodiment, but can be applied to other multi-cylinder engines, for example, a five-cylinder engine and a six-cylinder engine.

[0032]

As described above, according to the inventions of claims 1 to 3, it is possible to improve the output due to the intake dynamic effect over a wide operating range, and to exert the intake dynamic effect. The intake system can be made compact and lightweight with high rigidity, and is excellent in vehicle mountability.

[Brief description of drawings]

FIG. 1 is a vertical sectional side view taken along the line I-I of FIG. 3, showing an intake system for a multi-cylinder engine according to an embodiment of the present invention.

FIG. 2 shows the intake system of the multi-cylinder engine, which is shown in FIG.
It is a vertical side view in the II-II line.

FIG. 3 is a plan view in which a part of the intake device of the multi-cylinder engine is cut away.

FIG. 4 shows the intake system of the multi-cylinder engine, which is shown in FIG.
FIG. 4 is an enlarged sectional view taken along line IV-IV.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Engine main body 4 ... Cylinder 6 ... Independent intake passage 8 ... Intake expansion chamber 8a ... 1st volume chamber 8b ... 2nd volume chamber 13 ... 2nd passage 14 ... Shutter valve

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hideo Nakayama 3-1, Shinchi, Fuchu-cho, Aki-gun, Hiroshima Prefecture Mazda Motor Corporation

Claims (3)

[Claims] 1. An intake device for a multi-cylinder engine in which an independent intake passage provided corresponding to each cylinder is connected downstream of the first volume chamber, and a branch provided at a midpoint of each independent intake passage. A second volume chamber that is connected to the other end of each of the branch passages and that communicates between the independent intake passages through the branch passages, and is provided in each of the branch passages, depending on the operating state of the engine. A multi-cylinder engine, comprising: a control valve that opens and closes to open and close a branch passage, and a passage wall of the independent intake passage constitutes a part of a wall that constitutes the second volume chamber. Intake device. 2. The control valve opens and closes according to the engine speed as an operating state of the engine, closes the branch passage in the low rotation range of the engine, and opens the branch passage in the high rotation range of the engine. The intake system for a multi-cylinder engine according to claim 1, wherein the intake system is provided. 3. The intake system for a multi-cylinder engine according to claim 2, wherein the control valve is opened and closed only in a region where the engine load is equal to or higher than a predetermined load.