Intake system for an internal combustion engine with supercharger

Abstract: In an internal combustion engine (1) with supercharger (16), there is provided synchronizing means for allowing a timing or timings for varying characteristics of kinetic supercharging effects of intake air to synchronize with a timing or timings for varying supercharging pressure by the supercharger. Reduction in engine torque at the time when the supercharging pressure is shifted, can be compensated by enhancement in the engine torque generated at the time when the characteristics of the kinetic effect is varied.

Description: This invention relates to an intake system for an internal combustion engine with supercharger according to the first part of claim 1. In recent years, considerable types of the internal combustion engines tend to be provided with any types of superchargers to supercharge intake air. In these superchargers, their supercharging pressures to be imposed on the intake air are generally limited in enhancing the pressure by some limiting factors involved with the characteristics of the engines. Taking the upper limits of the supercharging pressure into consideration in relation to engine speeds, in a low engine speed range, the supercharging pressures are to be limited for preventing knocking of engine, in a middle engine speed range, the supercharging pressures are to be limited for ensuring appropriate combustion pressures thereof, and in a high engine speed range, the supercharging pressures are to be limited for ensuring appropriate heat loads thereof. In these permissible supercharging pressures thus defined by these limiting tactors, the permissible supercharging pressures depending on heat load of the engine is, in general, in the lowest level. Therefore, in the conventional engines, the maximum supercharging pressures have been substantially selected on the basis of the permissible supercharging pressure depending on the heat loads of the engines. In the internal combustion engine with supercharger as set forth above, it has been proposed that intake systems of the engines are arranged to supercharge the intake air further with so-called kinetic supercharging effects of intake air (for example, Japanese Utility-Model Laid-Open Publication No. 62-49625). The kinetic effect is intended to improve the volumetric efficiency of cylinders of engine so as to enhance the torque of the engine, and includes an inertia effect of intake air and a resonance effect of intake air. Since preferred nature of the kinetic effect can be obtained in syncronism with a certain engine speed, in the intake system to take the kinetic effect, it has been proposed that there is provided a means for allowing the intake system to correspond to different engine speeds, thereby taking the advantageous kinetic effect in a wide range of the engine speeds. For example, US-A-4,829,941 discloses one type of intake system having means for changing over the length of the resonance air column in the intake system on the basis of the engine speeds to obtain the advantageous resonance effect of intake air over a wide range of engine speeds, and further, the US-A-4,617,897 discloses another type of intake system which is adapted to change the length of and the cross-sectional area of the intake passage for obtaining a preferred inertia effect of intake air over a wide range of engine speeds, and furthermore, the US-A-4,651,684 discloses still another type of intake system in which the valve timing of intake valve is changed so as to vary the opening time thereof according to the operating condition of the engine whereby the volumetric efficiency is improved. Now, in the conventional engines with superchargers are previously mentioned, since the maximum value of the supercharging pressure provided by the supercharger has been settled on the basis of the limiting factor depending on the heat load of the engine, the engine can afford to enhance the supercharging pressures in the low and middle engine speed ranges. Therefore, it is taken into consideration that the maximum supercharging pressure is shifted in accordance with a parameter defined by engine speeds, that is, when, in simplification, the engine speed range is supposed to be divided into a relatively low range and a relatively high range, the maximum supercharging pressure is set into a high value in the low engine speed range and the maximum supercharging pressure is set into a low value in the high engine speed range, thereby changing over the maximum supercharging pressure between low and high value in accordance with the engine speeds. However, in such an arrangement, at the time when the maximum supercharging pressure is shifted, there is generated a great fluctuation in engine torque, that is, a torque shock and therefore, the approach to this problem has been required. From JP-A-60-104717 it is known that the engine comprises valves for changing the length of the air intake passage and means for varyably adjusting the closing timing of air intake valves, the latter including two types of cams. Further, the engine has means for controlling valves to close or open in correspondence to changing over from one type of cam to the other type of cam. From this document it is not known that the supercharging pressure imposed by a compressor of supercharging means is controlled. In JP-A-60-75721 a control apparatus for an internal combustion engine equipped with a supercharger comprising a first turbo charger, an inertial supercharging device, and a second supercharger, each of which is respectively operable according to high, medium and low rotational speed areas of the engine, detecting means for detecting for at least engine speed, selecting means for changing over the first turbo charger, the inertia supercharging device, and the second supercharger is known. It is an object of the present invention to provide an internal combustion engine with supercharger which can avoid the torque shock generated at the time when the maximum supercharging pressure of the supercharger is shifted. In accordance with the present invention there is provided an intake system for an internal combustion engine with supercharger with the features of claim 1. In accordance with the invention, reduction in torque generated at the time when the supercharging pressure is shifted, can be compensated by enhancement in the torque generated at the time when characteristics of kinetic effect of intake air vary. Thus, in an internal combustion engine with supercharger, an improved intake system which accomodates advantageously to both the functions of the supercharger and the kinetic effect of intake air can be obtained in other words, the torque curve of the engine can be improved as a whole so that it represents smooth torque curve without generating great fluctuation of the torque, namely torque shock upon the shift of the supercharging pressure. BRIEF DESCRIPTION OF THE DRAWINGS These and other objects and features of the invention will be more understood with reference to the following detailed description of illustrative embodiments of the invention, taken in connection with the accompanying drawings in which: Figure 1 is a schematic plan view illustrating diagramatically an internal combustion engine provided with an intake system in accordance with an embodiment of the present invention. Figure 2 is a graphical representation showing the characteristics in operation of the engine shown in Figure 1. Figure 3 is a graphical representation showing relationships among the limiting factors, maximum supercharging pressures and engine speeds for shifting the maximum supercharging pressure. Figure 4 is a schematic plan view illustrating diagramatically an internal combustion engine provided with an intake system in accordance with another embodiment of the present invention. Figure 5 is a schematic plan view illustrating diagramatically an internal combustion engine provided with an intake system in accordance with still another embodiment of the present invention. Figure 6 is a graphical representation showing a change in the valve timing of the engine shown in Figure 5 in relation to the crank angles. Description of the Preferred Embodiment Referring to Figure 1, an Otto-cycle four-cylinder engine 1 is shown therein, each of the cylinders C1-C4 of the engine 1 being provided with an intake port 2 and exhaust port 3. The intake ports 2 and the exhaust ports 3 are opened or closed in timed relations in synchronism with rotation of a crankshaft (not shown) of the engine by intake valves and exhaust valves (not shown), as well-known in the art. An intake passage 11 for introducing intake air into the cylinders C1-C4 has in its way a surge tank 12, which functions as a first pressure reflecting portion. The surge tank 12 is adapted to be supplied with the intake air through one common intake passage 13, which is provided with an air cleaner 14, an air-flow meter 15, a compressor 16a of a turbo-type supercharger (referred to as a "turbo-charger" hereinafter), and an inter cooler 17, one after another from an upstream side. The intake passage 11 is divided into two branch intake passages 18A and 18B on its downstream side of the surge tank 12, and the branch intake passages 18A, 18B are provided with throttle valves 19A, 19B respectively, which operate in an interlocked relation with each other. On a downstream side of the throttle valve 19A, the branch intake passage 18A individually communicates through discrete intake passages 20-1, 20-4 with each of the intake ports 2 of the first and forth cylinders C1, C4 which do not fire successively. Further, on a downstream side of the throttle valve 19B, the branch intake passae 18B individually communicates through discrete intake passages 20-2, 20-3 with each of the intake ports 2 of the second and third cylinders C2, C3 which do not fire successively. Each of the discrete intake passages 20-1∼20-4 is provided with a fuel injection valve 21. The branch intake passages 18A and 18B can be, on their end portions opposite to the surge tank 12, in communication with each other through a communicating passage 22 which functions as a second pressure reflecting portion, and the communicating passages 22 is provided with an on-off valve 23 which can open and close the communicating passage 22. The distance between each of the intake ports 2 and the surge tank 12 (the first pressure reflecting portion) taken along the discrete passage and the branch passage, is set to be larger than the distance between each of the intake port 2 and the communicating passage 22 (the second pressure reflecting portion) taken along the discrete and branch passages. Therefore, when the on-off valve 23 is closed, the surge tank 12 comes to act as the pressure reflecting portion and the resonance air column is set into relatively long length, whereby the length of the resonance air column can correspond to relatively low engine speed range for obtaining the proper kinetic effect of intake air therein. On the other hand, when said on-off valve 23 is opened, the communicating portion comes to act as the pressure reflecting portion 22 and the resonance air column is set into relatively short length, whereby the length of the resonance air column can correspond to relatively high engine speed range for obtaining the proper kinetic effect of intake air therein. Variations in the volumetic efficiency involved by such opening and closing of the on-off valve 23, are shown in Figure 2(a), in which the curve X1 represents the variation in a state where the on-off valve 23 is closed and the curve Y1 indicates the variation in a state where the on-off valve 23 is opened. Further, an exhaust passage 24 in communication with the exhaust ports 3 is joined into a single passage, and on the downstream side of the joined portion, a turbine 16b of said turbo-charger 16 is located. The turbine 16b is connected to said compressor 16a by means of a shaft 16c, so that the rotation of the turbine 16b by the energy of the exhaust air allows the compressor 16a to rotate to effect supercharging of the intake air. Still further, the exhaust passage 24 is provided with a by-path passage 25 bypassing the turbine 16b, in which a waste gate valve 26b is disposed for defining the maximum pressure of the supercharged intake air. The pressure for opening the waste gate valve 26 is adjusted by an actuator 31 reciprocating in responses to fluid-pressure. The actuator 31 has a first diaphragm 31b which defines a first chamber 31a and a second diaphragm 31d which defines a second chamber 31c, and the first and second diaphragms 31b, 31d are connected to the waste gate valve 26 by means of a shaft 32. The waste gate valve 26 is normally energized by a return spring 31e so as to close the by-path passage 25. The first chamber 31a normally communicates by way of a signal line 33 with the common intake passage 13 on the downstream side of the compressor 16a. The second chamber 31c is connected to the signal line 33 by way of a signal line 35 and a solenoid operated three way control valve 34 connected with the signal line 35. The control valve 34 has a first position in which the signal line 35 communicates with the signal line 33, and a second position in which a signal line 35 is released to the atmosphere. Therefore, when the control valve 34 takes the second position, the second chamber 31c is released to the atmosphere and the supercharging pressure provided by the turbo-charger 16 acts on only the first chamber 31a, so that the waste gate valve 26 is to be opened when the supercharging pressure reaches the first maximum supercharging pressure PM1 which is settled to be relatively high value. On the other hand, when the control valve 34 takes its first position, the supercharging pressure provided by the turbo-charger 16 acts on both the first and second chambers 31a, 31c, so that the waste gate valve 26 is to be opened when the supercharging pressure reaches the second maximum pressure PM2 which is settled to be relatively low value. These different maximum pressures PM1 and PM2 are indicated in Figure 2(c). Further, the on-off valve 23 is opened and closed by an actuator 36 reciprocating in responses to fluid-pressure. The actuator 36 has a diaphragm 36b which defines a chamber 36a, and the diaphragm 36b is connected to the on-off valve 23. The chamber 36a is in communication with a signal line 37 which branches from the signal line 35 downstream the control valve 34. Therefore, when the control valve takes the second position, the chamber 36a is released to the atmosphere so that the on-off valve 23 is closed. On the other hand, when the control valve 34 resides in the first position, the supercharging pressure acts on the chamber 36a so that the on-off valve 23 is opened. Thus, the on-off valve 23 is operated corresponding to a shift of the maximum supercharging pressures to vary the length of the resonance air column for obtaining desired kinetic effect of intake air, and the engine speed in which the maximum pressure is shifted and the on-off valve is operated, is referred to as a line E2 in Figure 2. In order to change over the positions of the control valve 34 on the basis of the engine speeds, there is provided a control unit U, and an engine speed signals is introduced into the control unit U from an engine speed sensor 38. The control unit U operates the control valve 34 in such a manner as above described when the engine speed reaches the value E2. In Figure 2b, torque curves of the engine are shown, which are provided by the aforementioned position control of the control valve 34. The curve X2 of the torque curves represents the engine torque in the case where the maximum supercharging pressure is set into PM1 and the resonance air column is set into relatively long length, and the curve Y2 of the torque curves represents the engine torque in the case where the maximum supercharging pressure is set into PM2 and the resonance air column is set into relatively short length. The engine speed E2 is to be selected so as to correspond to the intersection of the curve X2 and the curve Y2, and value of E2 in conventional type of engines is generally seleced to, for example 2500rpm ∼ 3000rpm. Further, the torque curve Z represented in Figure 2(b) by a phantom line indicates the engine torque in the case where the maximum supercharging pressure would be constantly set to be PM2 and the resonance air column would be set into relatively long length in overall engine speed range. Still further, the engine speed E1 shown in Figure 2(d) indicates an engine speed selected in accordance with conventional manner such that the length of the resonance air column is changed over at the engine speed for obtaining the appropriate kinetic effect of intake air with the maximum supercharging pressure kept in constant value. In Figure 3, there is shown how the aforementioned engine speed E2 and maximum supercharging pressure PM1, PM2 is selected in relation to limiting factors of the supercharging pressure for ensuring an appropriate operation of the engine. In Figure 3, a line α indicates a limiting line for preventing knocking of the engine, a line β indicates a limiting line for maintaining appropriate combustion pressure, and a line γ indicates a limiting line for ensuring appropriate heat load. It will be understood from the description as set forth above that, according to the present invention, when the maximum supercharging pressure is shifted in accordance with the engine speed ranges of the engine, the torque shock at the time of shifting the pressure can be prevented. Further, since the supercharging pressure can be enhanced in relatively low engine speed range, the advantageous torque in an Otto-cycle engine, can be ensured during operation thereof in the low engine speed range, and further in a diesel engine, the response thereof can be advantageously ensured particularly during quick accelerating. Figure 4 shows another embodiment according to the present invention, in which the members or mechanisms equal with the ones shown in Figure 1 are designated by the same reference numerals as used in Figure 1. In the present embodiment, there is provided a so-called mechanical-type supercharger which is mechanically driven by a crankshaft of engine. That is, a Roots-type supercharger 41 is disposed in a common intake passage 13, and the supercharger 41 is connected to the crankshaft of engine 1 by means of an electromagnetic clutch 42. A throttle valve 43 is disposed on the upstream side of the supercharger 41 in the common intake passage 13. On the downstream side of the throttle valve 43, the common intake passage 13 has a by-path passage 44 and a relief passage 45 arranged in parallel so as to be able to bypass the supercharger 41. The by-path passage 44 is provided with an on-off valve 46, and the relief passage 45 is provided with an on-off valve 47. The on-off valve 46, 47 and an on-off valve 23 disposed in a communicating passage portion 22 are adapted to be opened or closed by electromagnetic actuators 49, 50 and 48 respectively. Further, there is provided a control unit U, into which a signal from a supercharging pressure sensor 51 for sensing super charging pressure as well as a signal from an engine speed sensor 38, is inputted. In the engine 1 having the arrangement as above described, when the engine speeds is lower than a predetermined speed, that is, when the engine speeds reside in a range in which driving resistance of the supercharger is not extremely increased, the clutch 42 is operatively connected to drive the supercharger 41. Simultaneously, the on-off valve 23 as well as the on-off valve 46 is kept in its closed position so that a surge tank 12 defines a pressure reflecting portion to form a relatively long resonance air column. Further, as easily understood, the on-off valve 46 is kept in its closed position. On the other hand, when the engine speed is increased to higher level than the predetermined speed, the clutch 42 is released to disengage with the supercharger 41 so that supercharger 41 is not driven, and the on-off valve 23 is opened. This allows the maximum supercharging pressure to shift to low level (actually, supercharging effect by the supercharger 41 is not provided) and the resonance air column to change into short length. Further, as easily understood, while the supercharger 41 is not operated, the on-off valve 46 is forced to be opened. As set forth above, since the length of the resonance air column to obtain an advantageous kinetic effect of intake air, is changed over in synchronism with the switching of the supercharger 41 between operating state and unoperating state thereof, the torque shock generated in the engine 1 upon the switching therebetween can be prevented similarly to the aforementioned embodiment shown in Figure 1. In addition, the on-off valve 47 located in the relief passage 45 is opened in the case where, the supercharging pressure is extraordinarily increased for any reasons during operation of the supercharger 41. Alternatively, the on-off valve 47 may be used to shift the supercharging pressure during operation of the supercharger 41 in such a manner as the aforementioned embodiment shown in Figure 1, wherein the on-off valve 23 be operated to be opened or closed synchronously with the shift of the supercharging pressure by the on-off valve 47. Figure 5 shows still another embodiment in accordance with the present invention, in which the members or mechanisms corresponding to the ones shown in Figure 1 are designated by the same reference numerals as used therein. In an internal combustion engine 1 according to the present embodiment, there is provided valve timing control mechanism 60, which comprises a cam shaft assembly 61 for driving intake valves (not shown) to open and close intake ports 2, a sleeve 60a generally H-like shaped in its section and incorporated into the cam shaft assembly 61, and a shift lever 60b being adapted to be controlled by a control unit U. The cam shaft assembly 61 is divided into two protions 61a and 61b, with one being cam shaft associated with cams for driving intake valves, the other being a portion connected with a pulley 62 which is driven in rotation by a crankshaft (not shown) by means of a timing belt (not shown). The portions 61a, 61b is respectively formed at their opposite end portion with helical splines 63a, 63b, which are oriented in opposite directions, and internal peripheral portions of two flanges 60a₁ and 60a₂ of the sleeve 60a respectively engages with the helical splines 63a, 63b. The control unit U inputs control signals into the shift lever 60b. According to the engine 1 having such an arrangement, relative phase angle between the portions 61a and 61b of the cam shaft assembly 61, that is, relative phase angle between the cam shaft and the crankshaft (not shown) is controlled by the sleeve 60 so that the intake valves are opened and closed in accordance with valve timing shown by a solid line in Figure 6 when the engine speed resides in a low speed range less than a predetermined engine speed, that is, the intake valves are closed at relatively early timing in the low engine speed range. Therefore, the charging efficiency is enhanced in the low engine speed range and thus, the torque of engine varies substantially along a predetermined torgue curve such like the torque corve X2 shown in Figure 2(b). As the control unit U senses on the basis of the signals inputted from an engine speed sensor 38 that the engine speed is increased up to the predetermined engine speed, the control unit U outputs a control signal into the shift lever 60b and permits the shift lever 60b to move the sleeve 60 axially. Since the helical splines 63a and 63b is oriented in opposite directions, flanges 60a₁ and 60a₂ of the sleeve 60 allow the portions 61a and 61b of the cam shaft assembly 61 engaging therewith to rotate in opposite directions relatively to each other, so that the relative phase angle between the portions 61a and 61b, namely the one between the cam shaft and the crankshaft is changed and thereby, the timing for closing the intake valve is retarded as shown in a dotted line of Figure 6. Therefor, the changing efficiency is enhanced in the high engine speed range, and the engine torque varies substantially along a desired torque curve such like the torque curve Y1 shown in Figure 2(b). At the time when the valve timing is displaced so as to retard the timing for closing the intake valve, the control unit U permits a three way control valve 34 to operate an actuator 31 to shift the maximum permissible supercharging pressure to relatively low pressure. As can be understood from the aforementioned matters, in the present embodiment, since the valve timing control mechanism 60 displaces the valve timing for closing the intake valve to change the condition of intake air and at the same time, the waste gate valve 26 is opened or closed to shift the maximum supercharging pressure, high charging efficiency of intake air can be ensured over a wide range of the engine speeds and knocking of the engine can be prevented. Further, although in this embodiment, the relative phase angle between the cam shaft and the crankshaft is changed, thereby the valve timing being displaced in parallelism to change the valve timing for closing the intake valve, the lifting stroke may be changed to increase or decrease a period of opening time of the intake valve so as to change only the valve closing timing. Still further, in the embodiments as set forth above, the maximum supercharging pressure are set into two different pressures and the maximam pressure is stepwisely changed to either of them, but the maximum pressure may be set into three or more than three different pressurs which can respectively apply properly to the limiting lines shown in Fugure 3, and further, the length of resonance air column for obtaining the resonance effect may be changed over to three or more than three lengths Also, the manner for controlling the maximum supercharging pressure are described as to a manner wherein the waste gate valve adjust the exhaust air flow introduced into the turbine of turbine-type supercharger, and another manner wherein the connecting condition between the crank shaft of the engine and the compressor of the mechanical-type supercharger is changed (engaged or disengaged), but the other various manners for control the supercharging pressure as known in the art, for example, a manner wherein the relief passage relieves the supercharging pressure provided by the compressor of the mechanical-type supercharger can be adaptd in accordance with the present invention.

Claims: An intake system for an internal combustion engine with a supercharger, comprising: intake passage means (11) for introducing intake air into each of a plurality of cylinders of said engine (1) and providing a kinetic supercharging effect to the intake air, said passage means (11) having first intake passages (20-1, 20-2, 20-3, 20-4), each of which is individually connected with one of said cylinders and a second intake passage (13; 18A, 18B; 18) which is in communication with said first intake passages (20-1, 20-2, 20-3, 20-4), only one supercharging means having a compressor (16, 16a; 41) which is disposed in said second intake passage (13) for supercharging the intake air, first control means (34) for varying supercharging pressure according to operating conditions of said engine, second control means (23) for varying said kinetic supercharging effect so that volumetric efficiency is changed in accordance with the operating conditions of said engine characterized in that said supercharging means (16, 16a; 41) is controlled by a first controlling means (34) such that the maximum permissible supercharging pressure in a high engine speed range over a predetermined engine speed and including the maximum permissible engine speed of the engine is lower than the maximum permissible supercharging pressure in a low engine speed range below a predetermined engine speed, said intake passage means (11) is controlled by a second controlling means (23) so as to achieve a first kinetic supercharging effect in said low speed range and a second kinetic supercharging effect in said high speed range, said first (34) and second (23) control means are synchronized by sychronizing means so that the supercharging pressure is varied by said first control means (34) at the time when the volumetric efficiency is changed by said second control means (23). An intake system for an internal combustion engine with supercharger as defined in claim 1, wherein said supercharging means is a turbo-type supercharger (16) having a turbine (16b) which is disposed in exhaust passage means (24) of said engine (1) and which drives said compressor (16a) in rotation with rotation of said turbine (16b); said supercharing means (16) including by-path passage means (25) for bypassing exhaust air introduced into said turbine (16b), and a waste gate valve means (26) for adjusting cross-sectional area of said by-path passage means (25). An intake system for an internal combustion engine with supercharger as defined in claim 2, wherein said waste gate valve means (26) includes a valve body (32) and diaphragm means (31b, 31d) for displacing said valve body (32), said diaphragm means being associated with a chamber (31a, 31c), the fluid pressure in said chamber allowing said diaphragm means to displace said valve body so that said valve means (26) adjust the cross-sectional area, whereby the maximum permissible supercharging pressure is set into a first pressure or a second pressure. An intake system for an internal combustion engine with supercharger as defined in claim 1, wherein said supercharging means comprises a mechanical-type supercharger (41) which is arranged to drive a compressor in rotation with rotation of a crankshaft of said engine. An intake system for an internal combustion engine with supercharger as defined in claim 4, wherein said supercharging means (41) further comprises clutch means for bringing said compressor into operative engagement or disengagement with said crankshaft, and clutch control means for controlling said clutch means, said clutch control means allowing said clutch means to engage said compressor with said crankshaft when the engine speeds reside in relatively low engine speed range less than a predetermined engine speed, whilst said clutch control means allowing said clutch means to disengage said compressor with said cam shaft when the engine speeds reside in relatively high engine speed range over the predetermined engine speed. An intake system for an internal combustion engine with supercharger as defined in claim 4, said supercharging means further comprises relief passage means (45) for allowing a portion of said intake passage means on a downstream side of said compressor to communicate with a portion thereof on an upstream side of said compressor, and relief valve means (47) for controlling cross-sectional area of said relief passage means (45), said relief valve means (47) being controlled so as to vary the supercharging pressure on the basis of the engine speeds. An intake system for an internal combustion engine with supercharger as defined in claim 1, wherein said second intake passage includes a common intake passage (13) being provided with said compressor and two branch intake passages (18a, 18b) divided from a downstream portion of said common intake passage (13), one of said branch intake passages (18A) communication with predetermined first intake passage or passages (20-1, 20-4), the other of said branch passages communicating (18B) with the other first passage of passages (20-2, 20-3), said varying means including a communicating passage portion (22) communicating with each of the said branch intake passages (18A, 18B) valve means (23) for permitting one of said branch intake passages to communicate with the other thereof. An intake system for an internal combustion engine with supercharger as defined in one of the clams 1-7, wherein said varying means (23) is arranged to change the length of resonance air column. An intake system for an internal combustion engine with supercharger as defined in one of the claims 1-8, wherein said varying means comprises means for changing closing timing of intake valves disposed in said cylinders. An intake system for an internal combustion engine with supercharger as defined in one of the claims 1-9, wherein the torque of said engine involved by said characteristics of kinetic effect of intake air has two peaks of the torque, each of the peaks being generated at different two engine speeds, the engine torque being reduced in a engine speed range between the two engine speeds, a engine speed at which the lowermost torque is generated between the two engine speeds, existing in the low engine speed range. An intake system for an internal combustion engine with supercharger as defined in one of the claims 1-10, wherein said control means includes a first actuator which is adapted to operate in accordance with an electrical signal so as to vary the pressure of intake air provided by said supercharger into different pressure, said varying means includes a second actuator which is adapted to operate in accordance with an electrical signal so as to change the characteristics of kinetic effect of intake air into desired characteristics, and said synchronizing means includes controller means for outputting said electric signals into said first and second actuators simultaneously. An intake system for an internal combustion engine with supercharger as defined in claim 11, wherein said first and second actuator is adapted to operate in accordance with a single signal inputted from said controller means.

Inventors: HINATASE FUMIO, HITOMI MITSUO, NISHIKAWA TOSHIO, TAKEUCHI NOBUO, HINATASE, FUMIO, HITOMI, MITSUO, NISHIKAWA, TOSHIO, TAKEUCHI, NOBUO
Applicants: MAZDA MOTOR, MAZDA MOTOR CORPORATION
Application year: 1989
Main classification: F02B33
IPC codes: F02B37, F02B27, F02B39, F02B33, F02B75, F02D13, F02B1