JPH0788777B2 - Engine supercharger - Google Patents

Description

The present invention relates to an engine supercharger.

(Prior Art) Conventionally, a method of utilizing an inertial effect of intake air is widely known as a method of increasing intake air charging efficiency of an engine. Here, the inertial effect of intake air means that an intake negative pressure wave generated in the intake passage due to the downward movement of the piston during the opening of the intake port in the intake stroke propagates into the intake passage, and the pressure reversal portion having a predetermined volume is generated. The pressure reversal in (1) results in a positive pressure wave, which acts on the intake port portion immediately before the closing of the intake port and forcibly pushes the intake air into the combustion chamber (supercharging effect).

By the way, such an inertial effect of the intake air becomes better as the pressure amplitude of the negative pressure wave of the intake air generated in the intake passage becomes larger. From this, as disclosed in, for example, Japanese Patent Laid-Open No. 60-65230, a control valve that opens the intake passage between the intake port and the pressure reversal portion of the intake passage later than the opening timing of the intake port. Is provided, and a large intake negative pressure wave is generated on the downstream side of the control valve due to the delayed opening of the control valve, whereby the inertia effect is further enhanced and a higher level supercharging effect is obtained. Are known.

However, in the case where the inertial effect is improved by delaying the opening of the control valve provided in the intake passage in this way, the level of the intake negative pressure wave is increased by delaying the opening of the control valve for the following reasons. Even if it is attempted, it is not possible to fully utilize this practically, and there is a concern that problems such as an increase in operating noise due to an increase in intake noise may occur. That is, since the volume of the pressure reversal portion corresponding to the level of the intake negative pressure wave is required to effectively generate the inertial effect, the level of the intake negative pressure wave is increased by, for example, delaying the opening of the control valve as described above. If it is designed, the volume of the pressure reversal part will correspondingly increase, and it will not be possible to meet the demand on the engine layout to install the engine device in the relatively narrow and limited space of the engine room,
Therefore, in reality, the volume of the pressure reversal portion is set to be slightly smaller than the volume required from the pressure level of the negative pressure wave, and the inertia effect and the engine layout property are coordinated. Therefore, the intake inertial performance of the intake system could not be fully utilized, leaving some dissatisfaction with the output characteristics of the engine.

Further, when the volume of the pressure reversal portion is set to be slightly smaller than the pressure level of the negative pressure wave, the negative pressure wave which has not been pressure reversal in the pressure reversal portion exceeds the pressure reversal portion and further in the intake upstream side. Will be propagated to the side and generate a loud intake noise.

(Object of the Invention) The present invention has been made in view of the problems pointed out in the above-mentioned prior art section.
It is an object of the present invention to achieve an improvement in supercharging effect and a reduction in intake noise at the same time in a supercharging device for an engine designed to increase the intake charge amount by utilizing the inertial effect of intake air.

(Technical background of the invention) In view of the above-mentioned circumstances, the inventors of the present invention have provided an inertial effect in an engine supercharging device in which an inertial effect is increased by delaying the opening of a control valve provided upstream of an intake port. In the process of researching a method for achieving both effective use of intake air and reduction of intake noise, the excitation function of intake air (that is,
As disclosed in Japanese Patent Laid-Open No. 60-185027, a partition wall provided so as to block the intake passage and the exhaust passage in the middle of a pressure conduit provided across the intake passage and the exhaust passage and vibrates due to pressure pulsation of exhaust gas. Is provided, the intake air is vibrated by the vibration of the partition wall, and attention is paid to the action of generating or amplifying the pressure pulsation of the intake air in the intake passage, and the high-level pressure pulsation due to the vibration action of the intake air is generated. The inventors have come up with a method of forcibly reversing the negative pressure wave in the pressure reversal section by utilizing it, and have developed a concrete means thereof.

(Means for Achieving the Purpose) As a means for achieving the above object, the engine supercharging device of the present invention includes an intake port and an exhaust port which are opened and closed in synchronization with the rotation of the engine, and the intake port is provided. An intake passage and an exhaust passage connected to the exhaust port, and the intake passage has an intake delay opening means for starting intake after a lapse of a predetermined period from the intake top dead center of the engine, and a predetermined volume. A pressure reversing unit located on the intake upstream side of the intake retarding means for reversing the pressure of the intake negative pressure wave generated at the start of intake is further provided, and the pressure reversing unit and the exhaust passage are communicated via a pressure conduit, The pressure reversal portion is arranged in a state where communication between the intake passage and the exhaust passage is cut off, and oscillates intake air by vibrating due to pulsation of exhaust pressure transmitted through the pressure conduit. It is characterized in that an intake excitation device for exciting is provided.

(Operation) In the present invention, by the above-mentioned means, the intake air is excited by the intake vibration device provided in the pressure reversal portion, and the positive pressure of the pressure pulsation causes a part of the negative pressure wave transmitted in the pressure reversal portion. Since the pressure is forcibly inverted to the positive pressure, the substantial amount of the pressure inversion of the negative pressure wave is represented by the sum of the volume effect of the pressure inversion portion and the above-mentioned vibrating action. Therefore, (1) Even if the volume of the pressure reversing section itself is kept relatively small for reasons of engine layout, a higher level is achieved with a smaller volume of the pressure reversing section than when only the volume effect of the pressure reversing section is used. It is possible to cope with the pressure reversal of the intake negative pressure wave of (2) Since the pressure reversal capacity itself in the pressure reversal section increases, the negative pressure wave that propagates upstream beyond the pressure reversal section without pressure reversal is possible. As few as possible, Generation of intake noise caused by the propagation of pressure waves can be prevented as much as possible, effects and the like are obtained.

(Embodiment) A preferred embodiment of the present invention will be described below with reference to FIGS. 1 and 2.

(First Embodiment) FIG. 1 shows a system diagram of an intake / exhaust system of a four-cylinder vehicle engine equipped with a supercharging device according to a first embodiment of the present invention. Reference numeral 1 is an engine body. The intake ports 3A, 3B, 3C, 3D of the four cylinders 2A, 2B, 2C, 2D of the engine body 1 have independent intake passages 5A, 5
B, 5C, 5D are connected. Further, each of the independent intake passages 5A, 5B, 5C, 5D is gathered on the upstream side by the intake main passage 6, and together with the intake main passage 6, the intake passage 7
Are configured.

On the other hand, independent exhaust passages 8A, 8B, 8C, 8D are connected to the exhaust ports 4A, 4B, 4C, 4D of the cylinders 2A, 2B, 2C, 2D, respectively. The respective independent exhaust passages 8A, 8B, 8C, 8D are gathered by an exhaust collecting passage 9 on the downstream side thereof, and constitute an exhaust passage 10 together with the exhaust collecting passage 9.

Furthermore, each independent intake passage 5A, 5B, 5C, 5D of the intake passage 7
A control valve 16 is provided at the collecting portion of. This control valve
Reference numeral 16 denotes a means for delaying intake air in the scope of claims, and the independent intake passages 5A, 5B, 5C, 5 are provided on the outer peripheral wall thereof.
It is composed of a cylindrical body in which communication ports 17A, 17B, 17C, 17D capable of communicating with D respectively are formed with a predetermined phase angle.
The control valve 16 is stretched between a drive side wheel 21 attached to the output shaft 19 of the engine body 1 and a driven side wheel 22 attached to one end side of the control valve 16 via an advance device 20 described later. The output shaft 19 is rotatably driven via the provided belt 27. Therefore, with the rotation of the control valve 16, the respective communication ports 17A, 17B, 17C, 17D are communicated with or cut off from the corresponding independent intake passages 5A, 5B, 5C, 5D, respectively. , 2B, 2C, 2D are opened or closed.

The advance device 20 is a driving side helical gear 23 mounted on the driven side wheel 22 side, a driven side helical gear 24 mounted on the control valve 16 side and having a twisting direction opposite to the driving side helical gear 23, The drive side helical gear
23 and the driven-side helical gear 24 both mesh and
It has an adjusting piece 25 that is relatively displaceable in the axial direction with respect to 23, 24. Therefore, when the diameters of the drive side wheel 21 and the driven side wheel 22 are set so that the drive side helical gear 23 is synchronously rotated in the same phase as the output shaft 19 of the engine body 1, the adjustment piece 25 is moved in the axial direction by the actuator 26. To the driving side helical gear
23 and the rotational phase of the driven helical gear 24, that is, the output shaft 19
The rotation phase between the control valve 16 and the control valve 16 changes, and as a result, the angular cylinders 2A, 2
B, 2C, 2D intake ports 3A, 3B, 3C, 3D opening timing and control valve
The opening timing of each of the 16 communication ports 17A, 17B, 17C, 17D (that is, the opening timing of the control valve 16) is relatively changed.

The control valve 16 is opened later than the intake ports 3A, 3B, 3C, 3D of the cylinders 2A, 2B, 2C, 2D (later opening of intake air) so that the control valve 16 is opened. This is for increasing the level of intake negative pressure on the downstream side. Therefore, basically, this control valve 16 has at least each communication port 17A,
17B, 17C, 17D are designed to be opened after the opening timing of the intake ports 3A, 3B, 3C, 3D of the corresponding cylinders 2A, 2B, 2C, 2D and after the intake top dead center of the engine. However, in this embodiment, the advance device 20 is further provided, and the advance device 20 controls the opening timing of the control valve 16 with respect to the opening timing of each intake port 3A, 3B, 3C, 3D. By relatively advancing (advancing operation) or retarding (advancing operation), the control valve 16 is designed to increase the effect of retarding the intake air. Specifically, the engine speed increases. Accordingly, the valve opening timing of the control valve 16 is advanced so that the valve opening timing approaches the opening timing of the intake ports 3A, 3B, 3C, 3D. This is due to the following two reasons.
(1) In the low engine speed range, the negative pressure level of the intake pressure on the downstream side of the control valve 16 caused by the delayed opening of the control valve 16 becomes smaller than that in the high engine speed range. In this case, it is necessary to delay the opening timing of the control valve 16 as much as possible to increase the negative pressure level of the intake pressure (the reason for the negative pressure level). (2) The pressure wave generated in the intake passage 7 In order to effectively use the intake inertia due to the improvement of the intake supercharging effect, the engine speed (that is, the number of tuning points) N (rpm) and the control valve 1
The intake ports 3A, 3B, 3C, 3D are substantially represented by the period in which the opening periods of the six corner communication ports 17A, 17B, 17C, 17D and the corresponding opening periods of the intake ports 3A, 3B, 3C, 3D overlap. Between the opening period (hereinafter referred to as the effective opening period) θe (deg) and the natural frequency ν (Hz) of the intake system, N = θe ・ ν / 6 (1) In order to establish this in a wider operating range (rotational speed range) of the engine (that is, to utilize the intake inertia), the opening timing of the control valve 16 should be increased as the engine speed increases. It is necessary to accelerate the valve opening timing to approach the opening timing of the intake ports 3A, 3B, 3C, 3D (the reason for using the intake inertia), for two reasons.

Further, in this embodiment, the present invention is applied to provide a pressure conduit 11 between the exhaust passage 10 and an intermediate position between the attachment position of the throttle valve 12 of the intake passage 7 and the attachment positions of the air flow meter 13 and the air cleaner 14. And a pressure reversal part 31 having a predetermined volume for reversing the negative pressure wave of the intake air generated at the communication ports 17A to 17D in the middle of the pressure conduit 11, and further, this pressure reversal part 31 is formed. An intake air vibration device 30 described later is incorporated therein. The intake vibration exciter 30 has a partition wall 32 provided in the pressure reversing portion 31 so as to block communication between the intake passage 7 and the exhaust collecting passage 9.
A bellows member 34 provided around the partition wall 32 and the partition wall 32.
And a spring 33 for elastically supporting the. This partition
The inside of the pressure reversal portion 31 is divided into two chambers by the 32 and the bellows member 34: an intake chamber 35 communicating with the intake passage 7 and an exhaust chamber 36 communicating with the exhaust passage 10. Therefore, the partition wall 32 of the intake vibration exciter 30 vibrates in response to the pressure pulsation of the exhaust gas introduced into the exhaust chamber 36, and acts to vibrate the intake air.

According to the supercharging device having the above-described configuration, in each cylinder 2A, 2B, 2C, 2D of the engine, first during each intake stroke, after each intake port 3A, 3B, 3C, 3D opened, after a predetermined period of time. Since each communication port 17A, 17B, 17C, 17D of the control valve 16 is opened, each independent intake passage 5A, 5B, 5C, 5D corresponding to each cylinder 2A, 2B, 2C, 2D
A higher level of intake negative pressure is generated in the inside than in the so-called natural intake when the control valve 16 is not provided. Each of these independent exhaust passages 8
The intake negative pressure in A, 8B, 8C, and 8D is determined by each communication port 17A,
It is transmitted as a negative pressure wave to the upstream side through the intake main passage 6 together with the openings of 17B, 17C and 17D, and is pressure-reversed in the intake chamber 35 of the pressure reversing portion 31 provided on the upstream side to become a positive pressure wave. The intake air is supercharged by being transmitted to each intake port 3A, 3B, 3C, 3D immediately before the blockage (realization of the inertial effect of the intake air). In this case, in parallel with the inertial effect of the intake air, intake air vibration is performed by the advance angle device 20, the pressure pulsation due to the intake air inertia is amplified, and the supercharging action due to the inertial effect is further enhanced ( Realization of the intake vibration effect).

By the way, in this case, each communication port 17A, 17B, 17C,
By delaying the opening timing of 17D behind the opening timing of each intake port 3A, 3B, 3C, 3D of the corresponding cylinder 2A, 2B, 2C, 2D, a strong negative pressure wave of large amplitude is generated in the intake passage 7. Therefore, in order to effectively reverse the pressure of all the negative pressure waves and effectively utilize the wave energy, it is necessary to increase the volume of the pressure reversal portion 31 correspondingly. However, since increasing the volume of the pressure reversing portion 31 may lead to an increase in the size of the engine device and impair the engine layout, in reality, the volume of the pressure reversing portion 31 is required according to the level of the negative pressure wave. The engine output performance is improved by supercharging and the engine layout performance is improved by downsizing the engine device in order to coordinate with each other.
Therefore, a part of the negative pressure wave generated in the intake passage 7 cannot be pressure-reversed in the pressure reversal section 31, and as a result, the output performance of the engine cannot be sufficiently brought out, or the pressure reversal section 31 As described above, there is a possibility that a negative pressure wave that has not undergone pressure reversal may propagate over the pressure reversal portion 31 to the upstream side of intake air and generate a large intake noise, or the like.

However, in this embodiment, the present invention is applied and the intake vibration device 30 is provided in the pressure reversal section 31 and the intake vibration device 30 is provided.
Therefore, the negative pressure wave propagating in the pressure reversal portion 31 can be forcibly reversed by the pressure pulsation due to the vibration effect of the intake air. Therefore, the negative pressure wave generated in the intake passage 7 is effective due to both the pressure reversal action due to the opening effect (volume effect) in the pressure reversal portion 31 and the pressure reversal action due to the intake vibration of the intake vibration exciter 30. The pressure will be reversed. Therefore, it is possible to reduce the volume of the pressure reversal portion 31 by the amount of pressure reversal due to the intake vibration, and it is possible to achieve both output performance of the engine and engine layout performance.

Further, since most of the large negative pressure wave generated in the intake passage 7 is pressure-reversed in the pressure reversal section 31, the negative pressure wave that passes through the pressure reversal section 31 and propagates to the intake upstream side is reduced as much as possible. The generation of intake noise is suppressed to that extent, and quiet operation of the engine is realized.

(Second Embodiment) FIG. 2 shows an intake / exhaust system diagram of a four-cylinder vehicle engine equipped with a supercharging device according to a second embodiment of the present invention. In contrast to the first embodiment in which the four independent intake passages 5A, 5B, 5C and 5D are gathered by one intake main passage 6, the fourth embodiment
The two cylinders 2A, 2B, 2C, and 2D are divided into two cylinder groups by the cylinders in which the ignition sequence is continuous, and each cylinder group is provided with a separate control valve and an intake vibration exciter. The same effect as the first embodiment is obtained.

As a specific configuration, the first cylinder 2A and the fourth cylinder 2D form the first cylinder group X ₁ , and the second cylinder 2B and the third cylinder 2C form the second cylinder group X ₂ , respectively. And a first control valve 71 and a first intake vibration exciter 51 in the intake passage 7 on the side of the first cylinder group X ₁ .
The second control valve 72 and the second control valve 72 are provided in the intake passage 7 on the second cylinder group X ₂ side.
Each of the intake vibration exciters 52 is provided. In addition, the exhaust chamber 36 of the first intake vibration exciter 51 is connected to the first independent exhaust passage 8A and the fourth independent exhaust passage 8D of the exhaust passage 10 via the first pressure conduit 61 so as to generate the second intake excitation. The exhaust chamber 36 of the vibration device 52 is connected to the second independent exhaust passage 8B and the third independent exhaust passage 8C via the second pressure conduit 62, respectively. Further, the first control valve 71 and the second control valve 72 are synchronously rotated by a pair of gears 73, 74 provided at one end thereof and meshing with each other. All other components are the same as the first
The same effects as those of the first embodiment are exhibited, and the description of the other members will be omitted by assigning the same reference numerals to the other members of the first embodiment. To do.

(Effects of the Invention) An engine supercharging device of the present invention includes an intake port and an exhaust port that are opened and closed in synchronization with rotation of the engine, and connects an intake passage to the intake port and an exhaust passage to the exhaust port. On the other hand, in the intake passage, an intake delay opening means for starting intake after a lapse of a predetermined period from the intake top dead center of the engine, and an intake start having a predetermined volume and located upstream of the intake delay opening means A pressure reversal section for reversing the pressure of the intake negative pressure wave that sometimes occurs is provided, and the pressure reversal section and the exhaust passage are communicated with each other via a pressure conduit, and the intake passage and the exhaust passage are provided in the pressure reversal section. Is provided in a state where the communication of the above is cut off, and an intake vibration device that vibrates the intake air by vibrating by the pulsation of the exhaust pressure transmitted through the pressure conduit is provided.

Therefore, according to the supercharging device for an engine of the present invention, the intake air is excited by the intake vibration device provided in the pressure reversal unit, and the positive pressure of the pressure pulsation thereof causes one of the negative pressure waves transmitted to the pressure reversal unit. Since the portion is forcibly pressure-reversed to the positive pressure, the substantial pressure reversal amount of the negative pressure wave is represented by the sum of the volume effect of the pressure reversal portion and the vibrating action,
Therefore, (1) Even if the volume of the pressure reversal section itself is kept relatively small for reasons of engine layout, it is more effective in the pressure reversal section having a smaller volume than when only the volume effect of the pressure reversal section is used. It is possible to deal with the pressure reversal of the high-level intake negative pressure wave, and to realize the higher level supercharging effect by fully utilizing the inertial effect capacity of the intake system's intake. (2) In the pressure reversal section Since the pressure reversal capability itself increases, the negative pressure wave that propagates upstream beyond the pressure reversal part without pressure reversal is reduced as much as possible, and the generation of intake noise due to the propagation of the negative pressure wave is also possible. Therefore, it is possible to obtain an effect such as quiet operation of the engine is realized.

[Brief description of drawings]

FIG. 1 is a system diagram of an intake / exhaust system of an engine equipped with a supercharging device according to a first embodiment of the present invention, and FIG. 2 is equipped with a supercharging device according to a second embodiment of the present invention. It is a system diagram of an intake / exhaust system of the engine. 1 ... Engine body 2A-2D ... Cylinder 3A-3D ... Intake port 4A-4D ... Exhaust port 5A-5D ... Independent intake passage 6 ... Intake main passage 7 ... Intake passage 8A-8D ... Independent Exhaust passage 9 ...... Exhaust collecting passage 10 ...... Exhaust passage 11,61,62 ...... Pressure conduit 16,71,72 ...... Control valve (intake intake retarding means) 17A to 17D ...... Communication port 20 ...... Advance device 30,51,52 …… Intake vibration exciter 31 …… Pressure reversal part 32 …… Differential wall 33 …… Spring 34 …… Bright bellows member 35 …… Intake chamber 36 …… Exhaust chamber

Claims (1)

[Claims] Claim: What is claimed is: 1. An intake port and an exhaust port which are opened and closed in synchronization with the rotation of an engine. An intake passage is connected to the intake port and an exhaust passage is connected to the exhaust port. Intake delay opening means for starting intake after a lapse of a predetermined period from the intake top dead center, and pressure for inverting the pressure of an intake negative pressure wave having a predetermined volume and located upstream of the intake delay opening means at the start of intake An inversion section is provided, the pressure inversion section and the exhaust passage are communicated with each other through a pressure conduit, and the intake passage and the exhaust passage are disconnected from each other in the pressure inversion section. A supercharging device for an engine, comprising: an intake vibration device that vibrates due to pulsation of exhaust pressure transmitted through the pressure conduit to vibrate intake air.