JP2007205198A - Intake device for internal combustion engine - Google Patents

Abstract

In an intake device 10 of an internal combustion engine 1 having an even-numbered cylinder # 1 to # 6 group in a row, it is possible to improve intake performance and torque characteristics in a whole rotation range from a low speed to a high speed with a relatively simple configuration. To do.
A single surge tank 12 is connected in communication with the same number of individual intake passages 11a to 11f as cylinders # 1 to # 6. The internal space of the surge tank 12 is changed by the valve 13 into a single space or two rooms 12A and 12B. When the two rooms 12A and 12B are used, the individual intake passages 11a to 11f are divided into two sets, each being half of the group in the cylinder arrangement direction. Two resonators 17 and 18 associated with the two rooms 12A and 12B are attached to the outside of the surge tank 12. Two resonators 17 and 18 are connected adjacently in the cylinder arrangement direction. The communication pipes 19 and 20 extending from the two chambers 12A and 12B of the surge tank 12 are individually inserted into the two resonators 17 and 18.
[Selection] Figure 1

Description

  The present invention relates to an intake device used in, for example, an internal combustion engine mounted on a vehicle such as an automobile.

  For example, in a multi-cylinder internal combustion engine, when the number of cylinders is an even number, there is a tendency that all cylinders are divided into two groups by half and two independent intake devices are used for each group (for example, Patent Documents). 1 and 2).

  First, in the conventional example of Patent Document 1, in an in-line six-cylinder structure internal combustion engine, three cylinders are divided into two groups in the arrangement direction, and two systems of intake devices are provided in each group.

  In this two-system intake device, the upstream merging portions of the two intake manifolds having a three-pronged shape are individually connected to the two resonance chambers, and the two resonance chambers are connected to each other through the individual resonance passages. The configuration is such that the resonance frequency of the resonance chamber can be changed by an electromagnetic vibrator in communication with the buffer chamber.

  In the conventional example of Patent Document 2, in an internal combustion engine having a V-type six-cylinder structure, two independent intake systems are attached to every two banks provided with three cylinders.

  In this two-system intake system, two surge tanks are connected to two banks via individual intake passages, and both surge tanks are connected to each other via a communication passage. The communication passage is connected to a communication state and a non-communication state. A first opening / closing valve for switching is provided, and the resonance chambers are individually connected to the two surge tanks through passages, and a first state for switching the passages between a communication state and a non-communication state. 2 open / close valves are provided.

In the conventional example of Patent Document 2, the first and second on-off valves are appropriately controlled to open and close in accordance with the rotational speed of the internal combustion engine, so that resonance supercharging and inertia supercharging are performed. While obtaining high volumetric efficiency in the entire engine rotation range, the characteristics are smoothed to improve the torque characteristics.
Japanese Utility Model Publication No. 58-14425 Japanese Patent Laid-Open No. 4-36022

  In the conventional example of the above-mentioned Patent Document 1, since the buffer chamber is provided apart from the resonance chamber and is connected in communication with the resonance passage, the capacity of the resonance chamber is set when the resonance frequency of the resonance chamber is initially set. In addition, the cross-sectional area and length of the resonance path are adjusted. However, if the resonance path is lengthened, the occupied space becomes large, which is not preferable. In addition, in order to be able to adjust the resonance frequency of the resonance chamber according to the rotational speed of the internal combustion engine, an electromagnetic vibrator is used, and an actuator and a control device for controlling the operation of the electromagnetic vibrator are provided. It is pointed out that the equipment cost increases because it is necessary.

  Note that the conventional example of Patent Document 2 has a structure in which an independent intake device is provided for each of two banks in an internal combustion engine having a V-type six-cylinder structure, and the premise of the invention is different from the present invention. In this conventional example, in order to improve the intake performance in the entire rotation range of the internal combustion engine, one first on-off valve and two second on-off valves are used. It is pointed out that the equipment cost increases because an actuator and a control device for controlling the operation of each valve are required.

  An object of the present invention is to make it possible to improve intake performance and torque characteristics in the entire rotation range from a low speed to a high speed in an internal combustion engine with a relatively simple configuration in an intake device for an internal combustion engine.

  The present invention relates to an individual intake passage individually connected to each intake port of an even number of cylinder groups arranged in a line in an internal combustion engine, a single surge tank connected to each individual intake passage, and a surge tank Equivalent to two chambers of the surge tank and a valve for changing the internal space of the chamber into a single room or two rooms partitioned to divide the individual intake passage group into two sets by half in the cylinder arrangement direction Each of the air intake devices including two external air introduction passages that are individually connected to each other, and are adjacently coupled in the cylinder arrangement direction outside each region corresponding to the two chambers of the surge tank. Two resonators are directly attached, and the two chambers and the two resonators are individually connected to the areas corresponding to the two chambers of the surge tank by individually entering the two resonators. Communicating pipe connecting communicating is characterized by being provided.

  In this configuration, when the valve is closed, the internal space of the surge tank is partitioned into two rooms, so that two outside air introduction paths, two rooms in the surge tank, and two sets of individual intake path groups Two relatively long intake passages are secured, and resonance supercharging is performed by each of the two intake passages.

  In addition, in this state where the valve is closed and the internal space of the surge tank is partitioned into two chambers, fluctuations in the intake pressure in the two chambers of the surge tank can be individually attenuated by the two resonators. It helps to increase the supercharging effect.

  On the other hand, when the valve is opened, the internal space of the surge tank becomes a single space that is relatively large, so that the air introduced into the surge tank from the two outside air introduction passages is individually supplied to each cylinder only by the individual intake passages. A short intake passage to be supplied to the cylinder is secured, and inertia supercharging using the intake inertia of each cylinder is performed by the intake passage for each cylinder.

  For example, if the resonance supercharging is set to be performed in, for example, a low / medium speed rotation region of an internal combustion engine, and the inertial supercharging is performed in a high speed rotation region, the effect of resonance supercharging and inertial supercharging are performed in the medium speed rotation region. Both the effect of salary will be weakened.

  Therefore, in this medium speed rotation range, it is possible to improve the intake efficiency and torque by initially tuning the resonator so that a disturbing pressure wave is removed by the resonator so as to give a high pressure wave when the intake valve closes. It becomes possible. As a result, it is possible to obtain a flat high torque characteristic in which the resonance supercharging peak and the inertia supercharging peak are connected in the entire rotation range from low speed to high speed in the internal combustion engine.

  As described above, the intake device of the present invention has a configuration in which two resonators are directly attached to the outside of the surge tank, and a communication pipe for connecting and connecting them is inserted into the resonator. The electromagnetic vibrator as described in (Patent Document 1), the second on-off valve as described in the conventional example (Patent Document 2), the actuator for controlling the operation thereof, and the control system become unnecessary. This is advantageous in reducing costs.

  In addition, the initial tuning of the resonator, that is, the natural frequency of the resonator can be adjusted as appropriate depending on the capacity and the cross-sectional area and length of the communication pipe, but according to the target frequency (the rotational speed of the internal combustion engine). Set as appropriate. In particular, regarding the length adjustment of the communication pipe, it is possible to make it as long as possible within a range that does not protrude outside from the relationship of inserting and arranging it in the resonator, so a large occupied space is secured. It is possible to improve the mountability of the intake device because it is not necessary.

  Preferably, a vibration film capable of transmitting pressure is provided in a connecting portion between the region corresponding to the two chambers in the surge tank and both resonators.

  According to this configuration, for example, in a state in which the valve is closed and the internal space of the surge tank is partitioned into two rooms, both chambers are connected via a resonator and a communication pipe that are directly attached to each other via a vibration film. To communicate with each other's rooms.

  Thereby, the pressure wave in one room can be transmitted to the other room with a predetermined time difference, so that when the pressure difference between the two rooms occurs, the pressure difference is reduced.

  Preferably, the two communicating pipes are extended to the other side so as to intersect with each other so that the two chambers in the surge tank are alternately connected to the resonator on the side not corresponding thereto. Is provided.

  According to this configuration, since the two communicating pipes are inserted into the alternating resonators, when it is necessary to set the communicating pipe to be long when performing the initial tuning of the resonator, the communicating pipe is allowed to jump out of the resonator. However, it can be made as long as possible in a compact state.

  As described above, since the length of the communication pipe can be extended without increasing the occupied space, it is advantageous in increasing the degree of freedom of initial tuning of the resonator within the limited occupied space.

  According to the present invention, it is possible to improve the intake performance and torque characteristics in the entire rotation range from a low speed to a high speed in an internal combustion engine with a relatively simple configuration.

  An embodiment of the present invention will be described below with reference to FIGS. In this embodiment, a gasoline engine having an in-line six-cylinder structure mounted on a vehicle such as an automobile is taken as an example of an internal combustion engine to be used for an intake device.

  That is, as shown in FIG. 1, the internal combustion engine 1 has an in-line six-cylinder structure in which even-numbered (six) cylinders (cylinders) # 1 to # 6 are arranged in a line.

  Pistons 3... Are inserted into the cylinders # 1 to # 6 of the cylinder block 2 so as to reciprocate. The cylinders # 1 to # 6 are surrounded by the upper end of each piston 3 and the cylinder head 4. Each space is defined as a combustion chamber 5.

  The cylinder head 4 is provided with an intake port 4 a and an exhaust port 4 b corresponding to each combustion chamber 5. Openings on the combustion chamber 5 side in the intake port 4a and the exhaust port 4b are opened and closed by an intake valve 6 and an exhaust valve 7, respectively.

  An intake device 10 is attached to each intake port 4a, and an exhaust manifold (not shown) is attached to each exhaust port 4b.

  Here, the configuration of an embodiment of the intake device 10 according to the present invention will be described in detail.

  The intake device 10 communicates with a plurality of (six) individual intake passages 11a to 11f individually connected to the intake ports 4a of the cylinder head 4 and to the upstream side of the individual intake passages 11a to 11f. And a single surge tank 12 connected thereto.

  The whole individual intake passages 11a to 11f may be expressed as an intake manifold.

  The internal space of the single surge tank 12 is selectively divided into a single wide space and two chambers 12A and 12B divided in the cylinder arrangement direction by a valve 13 installed in the center of the cylinder arrangement direction. It can be changed.

  In the two chambers 12A and 12B, the six individual intake passages 11a to 11f are divided into two groups each in half in the cylinder arrangement direction, and each group is connected and connected separately.

  In this grouping, when the ignition sequence of the internal combustion engine 1 having a six-cylinder structure is, for example, # 1 → # 5 → # 3 → # 6 → # 2 → # 4, it is assumed that the ignition sequence is not adjacent to each other. The cylinder groups can be divided into # 2 and # 3 cylinder groups and # 4, # 5 and # 6 cylinder groups.

  In addition, in the upper surface of the surge tank 12, two systems of the external air introduction paths 14 and 15 are individually connected to the region corresponding to the two rooms 12 </ b> A and 12 </ b> B.

  The two external air introduction paths 14 and 15 are merged on the upstream side in the introduction direction, and a throttle body 16 that is opened and closed based on an operation of an accelerator pedal (not shown) is installed at the merged portion. Although not shown, an air cleaner or the like is attached to the throttle body 16.

  The two resonators 17 and 18 are directly attached to the back side of the surge tank 12 (on the side of the anti-internal combustion engine 1) in association with the two chambers 12A and 12B in a state adjacent to the cylinder arrangement direction. Yes.

  In the area corresponding to the two chambers 12A and 12B on the back side of the surge tank 12 (on the side of the anti-internal combustion engine 1), communication pipes 19 and 20 are respectively provided so as to project. The two resonators 17 and 18 are individually inserted.

  Specifically, the first and second communication pipes 19 and 20 are alternately extended so as to cross toward the other side, and the first communication pipe 19 is connected to the second resonator 18 and the second communication pipe. 20 is provided in communication with the first resonator 17. In other words, the first and second communication pipes 19 and 20 are provided so as to alternately connect the two chambers 12A and 12B in the surge tank 12 to the resonators 17 and 18 on the side not corresponding to each other.

  Further, vibration films 21 and 22 are provided at the coupling portions of the first and second resonators 17 and 18 with respect to regions corresponding to the two chambers 12A and 12B of the surge tank 12, respectively.

  Specifically, the first diaphragm 21 enables pressure transmission between the first chamber 12A of the surge tank 12 and the first resonator 17, and the second diaphragm 22 Pressure transmission is enabled between the two chambers 12B and the second resonator 18.

  Since the first room 12A and the second resonator 18 are connected to each other via the first communication pipe 19, and the second room 12B and the first resonator 17 are connected to each other via the second communication pipe 20, both The vibration membrane 21.22 transmits pressure between the first chamber 12A and the second chamber 12B with a predetermined time difference.

  Next, an intake operation by the intake device 10 having the above-described configuration will be described.

  First, when the valve 13 is closed, the internal space of the surge tank 12 is partitioned into two rooms 12A and 12B, so that the two outside air introduction paths 14 and 15 and the two rooms 12A and 12B in the surge tank 12 are A relatively long two-system intake passage is secured by the group of individual intake passages 11a to 11f, so that resonance supercharging is performed by each of the two intake passages.

  In addition, in the state where the internal space of the surge tank 12 is partitioned into the two chambers 12A and 12B in this way, fluctuations in the intake pressure in the two chambers 12A and 12B of the surge tank 12 are individually performed by the two resonators 17 and 18. It can be attenuated and helps to increase the supercharging effect.

  Furthermore, in the above state, both the rooms 12A and 12B are connected to each other's rooms via the resonators 17 and 18 and the communication pipes 19 and 20 that are directly attached to the rooms 12A and 12B through the vibrating membranes 21 and 22, respectively. Since the communication is established, the pressure wave in one room can be transmitted to the other room with a predetermined time difference. Therefore, when a pressure difference occurs between the two chambers 12A and 12B, the pressure difference is reduced. The natural frequencies of the vibrating membranes 21 and 22 can be adjusted as appropriate depending on the elastic coefficient and the membrane mass, but are appropriately set according to the target frequency (the rotational speed of the internal combustion engine).

  On the other hand, when the valve 13 is opened, the internal space of the surge tank 12 becomes a single space that is relatively large. Therefore, the air introduced into the surge tank 12 from the two outside air introduction paths 14 and 15 is supplied to each individual intake path 11a. A short intake passage that is individually supplied to each cylinder # 1 to # 6 is ensured by only ˜11f, and this makes it possible to perform inertia supercharging using the intake inertia of each cylinder by the intake passage for each cylinder # 1 to # 6. To be done.

  Here, for example, the resonance supercharging is set, for example, in the low / medium speed rotation region of the internal combustion engine, and the inertia supercharging is performed in the high speed rotation region.

  In this case, both the effect of resonance supercharging and the effect of inertial supercharging are weakened in the medium speed rotation region, but in this medium speed rotation region, a high pressure wave is given at the timing when the intake valve 6 is closed. Thus, it is possible to improve the intake efficiency and torque by initially tuning the resonators 17 and 18 so that the disturbing pressure waves are removed by the resonators 17 and 18.

  As described above, when the resonators 17 and 18 are appropriately tuned while effectively making resonance supercharging and inertial supercharging compatible, the internal combustion engine 1 in the internal combustion engine 1 can be used as schematically shown in FIG. It is possible to improve volumetric efficiency in all rotation ranges from low speed to high speed, and it is possible to obtain flat high torque characteristics that connect the resonance supercharge peak and the inertia supercharge peak. Become.

  Note that the target frequency (revolution speed of the internal combustion engine) for resonance supercharging is appropriately set according to, for example, Ne1 in FIG. 5, and the target frequency (rotation speed of the internal combustion engine) for inertial supercharging is For example, it is set appropriately according to Ne2 in FIG. Further, the initial tuning of the resonators 17 and 18, that is, the natural frequency of the resonators 17 and 18 can be adjusted as appropriate depending on the capacity and the cross-sectional area and length of the communication pipes 19 and 20. The number of revolutions of the internal combustion engine) is appropriately set in accordance with, for example, Ne3 in FIG.

  In particular, the length adjustment of the communication pipes 19 and 20 is not only performed by inserting the communication pipes 19 and 20 into the resonators 17 and 18, but also by inserting two communication pipes 19 and 20 into the alternating resonators 17 and 18. This is advantageous in expanding the degree of freedom of initial tuning of the resonators 17 and 18 within a limited occupation space. Thereby, since it is not necessary to ensure a large space for the intake device 10, the mountability of the intake device 10 on the vehicle is improved.

  As described above, in this embodiment, the resonators 17 and 18 are directly attached to the outside of the two chambers 12A and 12B of the single surge tank 12, respectively, and are connected in communication within the resonators 17 and 18. And a simple structure in which vibration films 21 and 22 that do not require a drive source are provided at the coupling portion between the surge tank 12 and the resonators 17 and 18. In addition, since the electromagnetic vibrator and the second open / close valve as described in the conventional example are not used, an actuator and a control system for controlling the operation are not required, and the equipment cost is reduced as compared with the conventional example. it can.

  That is, in this embodiment, it is possible to improve the intake performance and the torque characteristics in the entire rotation range from the low speed to the high speed in the internal combustion engine 1 with a simple configuration as compared with the conventional example.

  Hereinafter, other embodiments of the present invention will be described.

  (1) The present invention is not particularly limited as long as the number of cylinders of the internal combustion engine 1 is an even number of six cylinders or more, and is not limited to a gasoline engine but may be a diesel engine. Furthermore, even if the internal combustion engine 1 has a V-type structure, if the number of cylinders in one bank is an even number of six or more, the intake device attached to the one bank is applied as the configuration described in the above embodiment. be able to.

  (2) In the above embodiment, the vibration films 21 and 22 are provided at the coupling portion between the surge tank 12 and the resonators 17 and 18, but for example, as shown in FIG. It is also possible to use simple partitions 21a and 22a without providing them. In this embodiment, the other configuration is the same as that of the above-described embodiment, and the description thereof is omitted.

  In this case, although the effect of reducing the difference between the intake pressure in the first chamber 12A of the surge tank 12 and the intake pressure in the second chamber 12B cannot be expected, fluctuations in the intake pressure in the first chamber 12A and the second chamber The point that the effect of attenuating the fluctuation of the intake pressure in 12B is obtained is the same as in the above embodiment.

  Therefore, it is considered that the torque-up effect in the region between the resonance supercharging peak and the inertia supercharging peak shown in FIG. However, it can be said that the intake performance and torque characteristics in the entire rotation range of the internal combustion engine 1 can be improved while having a simple configuration as compared with the conventional example.

  (3) In the above-described embodiment, an example is given in which the communication pipes 19 and 20 that connect the surge tank 12 side and the resonators 17 and 18 are crossed and inserted into the resonators 17 and 18 alternately. For example, as shown in FIG. 7, the communication pipes 19 and 20 are eliminated, the first diaphragm 21 is provided on the partition wall between the first chamber 12 </ b> A of the surge tank 12 and the first resonator 17, and the second It is also possible to adopt a form in which the second vibration film 22 is provided on the partition between the room 12B and the second resonator 18 respectively. In this embodiment, the other configuration is the same as that of the above-described embodiment, and the description thereof is omitted.

  In this case, it is not necessary to set the communication pipes 19 and 20 as compared with the above-described embodiment, so that it is possible to expand the design freedom for adjusting the effects of the resonators 17 and 18.

1 is a plan view showing a schematic configuration of an embodiment of an intake device for an internal combustion engine according to the present invention. It is a side view of the intake device shown in FIG. It is a figure which shows the state which looked at the intake device of FIG. 1 from the intake upstream side. FIG. 2 is a perspective view schematically showing a state where the communication pipe of the intake device of FIG. 1 is transmitted. It is a graph which shows the characteristic of the air intake apparatus shown in FIGS. FIG. 6 is a view corresponding to FIG. 1 in another embodiment of the intake device for an internal combustion engine according to the present invention. FIG. 6 is a view corresponding to FIG. 1 in still another embodiment of the intake device for an internal combustion engine according to the present invention.

Explanation of symbols

4a Intake port
5 Combustion chamber
10 Intake Device 11a-11f Individual Intake Path
12 Surge tank
12a Room 1
12b Second room
13 Valve
14 First outside air introduction path
15 Second outside air introduction path
17 First resonator
18 Second resonator
19 First communication pipe
20 Second communication pipe
21 First diaphragm
22 Second diaphragm

Claims (3)

An individual intake passage individually connected to each intake port of an even number of cylinders arranged in a line in the internal combustion engine;
A single surge tank connected to each individual intake passage;
A valve for changing the internal space of the surge tank into a single room or two rooms partitioned so that the individual intake passage group is divided into two groups by half in the cylinder arrangement direction;
An air intake apparatus including two external air introduction paths that are individually connected in communication with each region corresponding to the two rooms of the surge tank,
Two resonators adjacently connected in the cylinder arrangement direction are directly attached to the outside of each region corresponding to the two rooms of the surge tank,
Each region corresponding to the two rooms of the surge tank is provided with a communication pipe that individually connects the two rooms and the two resonators by individually entering the two resonators. An intake device for an internal combustion engine.   2. An intake system for an internal combustion engine according to claim 1, wherein a vibration film capable of transmitting pressure is provided in a connecting portion between the region corresponding to the two chambers in the surge tank and both resonators.   In Claim 1 or 2, the said both communicating pipes are extended to the other side, and are made into the state which cross | intersects, By staggering two chambers in a surge tank to the resonator of the side which does not respond | correspond to them. An intake device for an internal combustion engine, wherein the intake device is provided so as to communicate with each other.

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