Control system for internal combustion engine with turbo supercharger

Abstract: A control system for an engine with a turbe supercharger comprising first switching device (26) for switching an introduction of intake gas to the engine in accordance with engine speed between a first intake condition in which a charging efficiency of the intake gas is improved in a lower engine speed condition and a second intake condition in which the charging efficiency of the intake gas is improved in a higher engine speed condition, second switching device (18) for switching a maximum supercharging pressure of the turbo supercharger from a lower pressure to a higher pressure in response to a switching operation between the first intake condition and second intake condition. An improved charging efficiency of the intake gas can be obtained in a broader range of the engine speed reducing the maximum supercharging pressure of the intake gas, thereby preventing the knocking of the engine.

Description: BACKGROUND OF THE INVENTION Field of the invention The present invention relates to a control system for an internal combustion engine having a turbo supercharger. Description of the prior art From JP-A-60104717 there is already known an engine having a turbo supercharger, in which an air intake valve is provided, wherein in response to an operation of the intake valve the length of an air intake passage is changed. There is also known a dynamic supercharger utilizing a pressure oscillation or resonance effect of intake gas, valve timing control device for controlling valve timings of intake and/or exhaust valves and a mechanical and turbo super charger so that an improved intake gas charging efficiency can be obtained. Further there has been also known that a first intake condition in which the engine is controlled to improve the intake gas charging efficiency in a lower engine speed condition and a second intake condition in which the engine is controlled to improve the intake gas charging efficiency in a higher engine speed condition is selectively established in accordance with the engine speed to obtain an improved intake gas charging efficiency in a greater range of the engine speeds. In addtion, it has been proposed to combine two or more of the above control systems for further improving the intake gas efficiency. For example, Japanese Patent Public Disclosure No. 59-164408, laid open to the public in 1984, discloses an engine provided with both the turbo supercharger and the dynamic supercharger. In the engine with the turbo supercharger, it is desirable to suppress an excessive increase of the supercharging pressure of the intake gas in the lower engine speed condition in order to prevent a knocking. It should be however noted that there is no conventional engine with both the turbo supercharger and other system for improving the charging efficiency of the intake gas which can improve the charging efficiency preventing the knocking of the engine in a broader range of the engine operating condition. SUMMARY OF THE INVENTION It is therefore a primary object of the present invention to provide a control system which can improve the charging efficiency preventing the knocking of the engine in a broader range of the engine operating conditions. It is another object of the present invention to provide an engine provided with both the turbo supercharger and a system other than the turbo supercharger for improving the intake gas charging efficiency which can improve the charging efficiency preventing the knocking of the engine in the broader range of the engine operating condition. According to the present invention, in order to accomplish the above and other objects, there is provided a control system for an engine having a turbo supercharger according to claim 1 and claim 2. In a preferred embodiment of the present invention, the first switching device includes both the variable valve and the valve timing control device. The valve timing control device changes the introdction of the intake gas from the first intake condition to the second intake condition at an engine speed lower than an engine speed in which the variable valve changes the introduction of the intake gas from the first to second intake conditions. In still another preferred embodiment, the first switching device can be constituted by a volume changing device for changing a volume of the turbo supercharger. According to the present invention, a high charging efficiency of the intake gas can be maintained in a broader range of the engine speed reducing the maximum supercharging pressure of the intake gas, thereby preventing the knocking of the engine. The above and other features of the present invention will become apparent from the following description in connection with the preferred embodiment taking reference with the accompanying drawings. BREIF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic view of an intake and exhaust system of a four-cylinder engine with a resonance superchaging system and a turbo supercharger in accordance with a preferred embodiment of the present invention; Figure 2 is a graphical representation showing a relationship of engine speed, maximum supercharging pressure and the engine torque; Figure 3 is a schematic view of a four-cylinder engine with both valve timing control device and the turbo supercharger similar to Figure 1 but showing another embodiment; Figure 4 is a graphical represntation showing a change in an opening period of the intake valve; Figure 5 is a schematic view of a four-cylinder engine with both variable control device utilizing a resonance effect of the intake gas and the turbo supercharger similar to Figure 1 but showing still another embodiment; Figure 5A is a graphical representation showing a relationship of engine speed, maximum supercharging pressure and the engine torque similar to Figure 2 but showing the embodiment of the Figure 5; Figure 6 is a schematic view of a four-cylinder engine with two turbo supercharger in accordance with yet another embodiment of the present invention; Figure 7 is a schematic view of a four-cylinder engine with a turbo-supercharger having dual intake passages to a turbine thereof in accordance with further embodiment of the present invention. DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to Figure 1, a four-cylinder engine A in accordance with the present invention is provided with a first, second, third and fourth cylinders 1a, 1b, 1c and 1d respectively from one end of the engine A in a longitudial direction thereof. An ignition occurs in order of the first, second, third and fourth cylinders 1a, 1c, 1d and 1b. Intake ports of the first through fourth cylinders 1a∼ 1d are connected with independent intake passages 2a∼ 2d. The independent intake passages 2a and 2d of the first and fourth cylinders 1a and 1d which intake strokes do not take place continuously are connected with a merged intake passage 3a. Likewise, the independent intake passages 2b and 2c of the second and third cylinders 1b and 1c which intake strokes do not take place continously are connected another merged intake passage 3b. The merged intake passages 3a and 3b are communicated with each other through a communicating passage 4 at an upstream end and through a communicating passage 4 shorter than the communicating passage 5 at a downstream end. The downstream communicating passage 5 is provided with a variable intake valve 6. In an upstream portion of the merged intake passages 3a and 3b are disposed throttle valves 6a and 6b. A dimension of the upstream communicating passage 4 is so determined that an intake structure constituted by the independent intake passages 2a∼ 2d, the merged intake passages 3a and 3b and the communicating passage 4 provides a resonance supercharging effect around an engine speed n₀. The dimension of the downstream communicating passage 5 is so determined that an intake structure constituted by the independent intake passages 2a ∼ 2d, the merged intake passages 3a and 3b and the communicating passage 5produces a resonance supercharging effect around an engine speed n₁ wherein the engine speed n₁ is greater than the engine speed n₀. The upsteam portion of the communicating passage 4 is communicated with a compressor 8 of a turbo-supercharger B through an intercooler 7 for cooling superchaged air. In an upstream side of the compressor 8, the passage 4 is communicated withl an air flow meter 9 and an air cleaner 10. Exhaust ports of the first through fourth cylinders 1a∼ 1d are communicated with a merged exhaust passage 12. A downsteam portion of the merged exhaust passage 12 is communicated with an exhaust passage 14 through a turbine of the turbo supercharger B. There is provided a bypass passage bypassing the turbine 13. The bypass passage 15 is provided with a waste gate valve 16 therein for controlling an amount of exaust gas introduced into the tubine 13. The waste gate valve 16 is connected with an actuator 18 through a rod 17 to be opened and closed. The actuator 18 is provided with a large cylindrical portion 18a and a small cylindrical portion 18b. The large cylindrical portion 18a and the small cylindrical portion 18b are partitioned by diaphragms 19a and 19b to define chambers 18a₁, 18a₂, 18b₁ and 18b₂ respectively. A spring 20 is disposed in the chamber 18a₁, for urging the diaphragm 19a toward the chamber 18a₂. The chambers 18a₁ and 18b₂ are opened to the atmosphere. The rod 17 is fixed to the waste gate valve 16 and the diaphragms 19a, 19b and passes through an opening of the chamber 18a₁ through which the chamber 18a₁ is communicated with the atmosphere and an opening on a partition wall between the chambers 18a₂ and 18b₁. In this case, a sealing member is arranged to plug the opening of the partition wall to keep airtightness of the partition wall. The chamber 18a₂ of the large cylindrical portion 18a is communicated with the intake passage just downstream of the compressor 8 through a communicating passage 21. The chamber 18b₁ of the small cylindrical portion 18b is communicated with the communicating passage 21 through a communicating passage 22, a three-way solenoid 23 and a communicating passage 24. The three-way solenoid 23 is commnicated with a chamber 26a of an actuator for the variable intake control valve 6 through a communicating passage 25 which is separated from the communicating passaged 22. The chamber 26a is formed adjacent to a chamber 26b through a diaphragm 27. There is provided a spring 28 in the chamber 26b for urging the diaphragm 27 toward the chamber 26a. The chamber 26b is opened to the atmosphere . A rod 29 joined with the diaphragm 27 at one end is extended through an opening communicated with the atmosphere. The other end of the rod 29 is connected with a rotation shaft 6a of the variable intake control valve 6 through an appropriate rotation mechanism. The three-way solenoid 23 is so constituted as to take a first operating position in which the commumicating passages 22 and 25 are opened to the atmosphere and the communicating passage 24 is closed and as to take a second operating position in which the communicating passages 22 and 25 are communicated with the communicating passage 24 and the communicating passage 24 is opened. The three-way solenoid 23 is controlled by a control unit C which is provided with memory storing a control program, an input and output interface and CPU. The control unit C receives a signal from an engine speed sensor and produces a control signal to the thee-way solenoid 23. In operation, in an engine operating range of a lower engine speed in which the engine speed is lower than a predetermined engine speed N (n₁>N>n₀), the three-way solenoid is maintained at the first operating position. In this condition, the chamber 26a of the actuator 26 is opened to the atmosphere so that the the diaphragm 27 is displaced toward the chamber 26a due to a resilient force of the spring 28. The displacement of the diaphragm 27 is transmitted to the rod 29 which is joined with the diaphragm 27, to the rotation shaft 6a through the rotation mechanism and to the variable intake control valve 6 so that the variable intake valve 6 closes the communicating passage 5. Thus, the intake system for the resonance effect of the intake gas is constituted by the independent passages 2a∼2d, the merged passages 3a and 3b, and the communicating passage 4 wherein the resonance effect is obtained around the engine speed n₀ to impove the intake gas charging efficiency. As a result, the engine torque changes along a curved line I to take a peak value as shown in Figure 2 (first intake condition). In a condition where the engine is stopped, the diaphragm 19a of the actuator 18 is displaced toward the chamber 18a₂ due to a resilient force of the spring 20. The displacement of the diaphragm 19a is transmitted to the waste gate valve 16 through the rod 17 fixed to the diaphragm 19a so that the waste gate valve 16 closes the bypass passage 15. As the engine speed is increased after engine is started, the supercharging pressure of the turbo supercharger B. When the engine speed is greater than a predetermined value N₀(N₀<N), a force urging the diaphragm 19a toward the chamber18a₁ due to the supercharging pressure P₁ introduced from the intake passage downstream of the compressor 8 into the chamber 18a₂ through the communicating passage 21 overcomes the resilient force of the spring 20 urging the diaphragm 27 toward the chamber 18a₂ so that the waste gate valve 16 is opened to open the bypass passage 15. Thus, the supercharging pressure of the turbo supercharger B increases until the engine speed reaches the predetermined value N₀. When the supercharging pressure reaches a value P₁ that is, the engine speed reaches the value N₀, the waste gate valve 16 is opened to suppress the increase of the supercharging pressure. As a result, the supercharging pressure is maintained at the value P₁ even when the engine speed increases beyond the value N₀. When the engine speed is increased to reach the predetermined value N, the control unit judges the engine speed N based on the engine speed signal producing a control signal to the three-way solenoid 23 in order to establish the second operating position. The supercharging pressure P₁ from the intake passage downstream of the compressor 8 is introduced into the chamber 26a of the actuator 26 through the communicating passages 21, 24 and 25. The pressure P₁ in the chamber 26a urges the diaphragm 27 toward the spring 28. The force due to the pressure P₁ overcomes the resilient force of the spring 28 so that the variable intake control valve 6 opens the communicating passage. As the result, an intake system for the resonance effect of the intake gas constituted by the independent intake passages 2a ∼ 2d, the merged intake passages 3a and 3b is established to provide the resonance effect of the intake gas around the engine speed n₁ so that the charging efficiency of the intake gas is improved around the engine speed n₁ and thus the engine torque exerted by the engine changes along a curved line II as shown in Figure 2 to take a peak value (second intake condition). On the other hand, the supercharging pressure P₁ is also introduced into the chamber 18b₁ of the actuator 18 from the intake passage downsteam of the compressor 8 through the communicating passages 21, 24 and 22. A force is produced due to the pressure P₁ urging the diaphragm 19b toward the chamber 18b₂. A sum of the force due to the pressure P₁ and the resilient force of the spring urging the diaphragm 19b toward the chamber 18b₂ overcome the force due to the pressure P₁ introduced into the chamber 18a₂ through the communicating passage 21 for urging the diaphragm 19a toward the spring 20 so that the waste gate valve 16 is actuated to close the bypass passage 15. As a result, the supercharging pressure is abruptly increased. It should however be noted that the diaphragm 19a is greater than the diaphragm 19b in area. Thus, the supercharging pressure reaches a value P₂ (P₂>P₁), the force due to the pressure P₂ introduced into the chamber 18a₂ to urge the diaphragm 19a compressing the spring 20 overcomes the sum of the force due to the pressure P₂ introduced into the chamber 18b₁ and the resilient force of the spring 20 so that the waste gate valve 16 is actuated to open the bypass passage 15. As a result, the supercharing pressure is abruptly increased from the value P₁ to P₂ when the engine speed reaches the value N. Then the supercharging pressure is maintained at the value P₂. As aforementioned, according to the illustrated embodiment, the variable intake control is switched between the closed and opened position and the waste gate valve 16 takes the opened and closed position to change the maximum value of the supercharging pressure in accordance with the engine speed. As a result, the high charging efficiency of the intake gas can be obtained in a broader range of the engine speed preventing the knocking of the engine. Referring to Figure 3, there is shown a four cylinder engine with a supercharger in accordance with another embodiment of the present invention. The same elements as the former embodiment are referred to as the same reference numerals as the former embodiment and a detailed explanation thereto will be omitted. Independent intake passages 2a′ through 2′ are connected to a merged intake passage 3a′. There is provided an intake valve timing control device 30 for controlling an open and close timing of the intake valve. The control device 30 is provided with a cam shaft 31 for driving the intake valves, a sleeve 30a of a substantially H-shaped cross section incorporated into the cam shaft 31 and a drive lever 30b controlled by the control unit C. The cam shaft 31 is provided with a first portion 31a on which cam portions are formed and a second portion 31b connected with a pulley 32 which is driven by the crank shaft through a belt (not shown). The first portion 31a and second portion 31b are formed with herical splines 33a and 33b at one ends respectively facing to each other but oriented opposite to each other. The sleeve 30a is formed with a pair of flange portions 30a₁ and 30a₂ which are formed with a threaded opening brought into engagement with the splines 33a and 33b. The control unit C produces a contol signal to the drive lever 30b. With this structure, a relative angular relationship between the first portion 31a and the second portion 31b is so determined that the intake valve timing is advanced in a lower engine speed range (first intake condition). As a result, the charging efficiency of the intake gas is improved in the lower engine speed range and changes along a curved line I as shown in Figure 2. When the engine speed increased to reach a predetermined value, the control unit C produces a signal to the lever 30b so that the sleeve 30 is axiall moved. Thus, the first portion 31a and second portion 31b of the cam shaft 31 both engaged with the flange 30a₁ and 30a₂ produces a relative rotative movement therebetween because of the opposite orientation of the splines 33a and 33b. As a result, the relative angular relationship between the cam shaft 31 and the crank shaft is changed to retard the valve timing as shown by the real line in Figure 4 in which the charging efficiency is improved a higher engine speed range to change along a curved line II as shown in Figure 2 (second intake condition). On the other hand, on switching the valve timing from the advance timing to the retard timing, the control unit produces a control signal to the three-way solenoid 23 to switch the fisrt operating position to the second operating position so that the waste gate valve 16 is closed to increase the maximum supercharging pressure. As aforementioned, according to the illustrated embodiment, the intake valve timing control device 30 changes the valve timing of the intake vavle to change the intake condition, changing the maximum supercharging pressure by controlling the waste gate valve 16. An improved charging efficiency of the intake gas can be maintained in a broader range of the engine speed preventing the knocking of the engine. Although the relative angular relationship between the cam shaft and the crank shaft is changed in the above embodiment to change the intake valve timing for changing the intake condition, a valve lift can be changed to obtain the same effect. Referring to Figure 5, there is shown a four cylinder engine with a turbo supercharger in accordance with still further embodiment of the present invention. The illustrated engine is provided with the valve timing control device as explained in conncetion with Figure 3 in addition to the resonance supercharger as explained in connection with the embodiment of Figure 1. In this embodiment, the communicating passage 25 is not communicated with the communicating passage 22 but with the communicating passage 21 through a solenoid 23′ which can receive the signal from the control unit C. According to the illustrated embodiment, at least in a higher engine load condition, When the engine speed exceeds a value N1, the control unit C controls the three-way solenoid 23 to take the second operating position from the first operating position and the timing control device 30 to retard the valve timing. When the engine speed exceeds a value N2 which is greater than the value N1, the solenoid is controlled to introduce the supercharging pressure into the communicating passage 25 for thereby opening the communicating passage by opening the the variable valve 6. Thus, when the engine speed is lower than the value N1, the closing timing of the intake valve is advanced to improve the charging efficiency. When the engine speed is in range between the value N1 and N2, the closing timing of the intake valve is retarded to improve the charging efficiency. Further, when the engine speed exceeds the value N2, the resonance effect of the intake system including the merged intake passage 3a and 3b and the communicating passage 5 can be obtained to improve the charging efficiency. As a result, the engine torque changes as shown by curved lines III(first intake condition), IV(second intake condition) and V(third intake condition) in Figure 5A. When the engine speed is lower than the value N1, the supercharging pressure is maintained at a lower value P₃ so that the knocking is suppressed effectively. Although the maximum supercharging pressure is increased to a value P₄ when the engine speed exceeds the value N1, the close timing of the intake valve is retarded to reduce compression ratio of the intake gas to suppress the knocking. Taking reference to Figure 6, there is shown a six cylinder engine with a turbo supercharger in accordance with yet further embodiment of the present invention. In Figure 6, the engine A is provided with a first cylinder 101a, second cylinder 101b, third cylinder 101c, fourth cylinder 101d, fifth cylinder 101e and sixth cylinder 101f in this order from one end thereof in a longitudinal direction. The ignition take place in the order of the first cylinder 101a, the fifth cylinder 101e, the third cylinder 101c, the sixth cylinder 101f, the second cylinder 101b and the fourth cylinder 101d. Intake ports of the first through the sixth cylinders 101a ∼ 101f are connected with independent intake passages 102a∼ 102f which are connected to a merged intake passage 103. An upstream portion of the merged intake passage 103 is communicated with a compressor 106b of a first supercharger 106 through a throttle valve 104 and an intercooler 105. The intake passage upstream of the compressor 106b is biforked into two intake passages 107 and 108. The intake passage 107 is connected with a compressor 109b of a second compressor 109. The intake passage 107 is communcated with an air flow meter and an air cleaner 111. The intake passage 108 is communicated with the intake passage 107 upstream of the compressor 109b. The intake passage 108 is provided with a gate valve 112 to open and close the passage 108. Exhaust ports of the first cylinder 101a ∼ the sixth cylinder 101f are connected with a merged exhaust passage 114 through independent passages 113a ∼ 113f. The merged exhaust passage 114 is formed with a reduced portion between the independent passages 113c and 113d for preventing interference of the exhaust gas. Thus the merged exhaust passage 114 is divided by the reduced portion into a first merged exhaust passage 114a and a second merged exhaust passage 114b. The first merged exhaust passage 114a is communcated with a turbine 106a of the first supercharger 106. The second merged exhaust passage 114b is communicated with a turbine 109a of the second supercharger 109. There is provided a gate valve 115 in a joint portion between the first merged exhaust passage 114a and the turbine 106a. An exhaust passage portion downstream of the turbines 106a and 109a is connected with an exhaust passage 116. A waste gate valve 117a is disposed in a communicating portion between a bypass passage 117 and the second merged exhaust passage 114b. In order to operate the gate valve 112 and 115, there are provided with actuators 118 and 119. An actuator 120 is provided for operating the waste gate valve 117a. In order to take out the supercharging pressure for the actuators 118, 119 and 120, a communicating passage 121 is joined with the intake passage downstream of the compressor 106b of the first supercharger 106. A communicating passage 122 separated from the communicating passage 121 connected with the actuator 119 and a communicating passage 123 separated from the communicating passage 122 is connected with the actuator 118. Further, a communicating passage 124 separated from the communicating passage 124 is connected with the actuator 120. At a portion of the communicating passage 122 upstream of a merged point with the communicating passage 123 is diposed a three-way solenoid valve 125 which take a first positon for closing an upstream portion 122a of the passage 122 upstream of the solenoid valve 125 and for releasing a downstream portion 122b of the passage downstream of the solenoid valve 125 to the atmosphere and a second position for communicating the upstream portion 122a with the downstream portion 122b. The three-way valve 125 is controlled by the control unit C. In operation, when the engine is in a stopped condition or in a lower engine speed condition wherein the engine speed is lower than a predetermined value, the control unit C keeps the three-way valve 125 at the first position. In this condition, the communicating passage 122b is opened to the atmosphere so that the actuators 118 and 119 keep the gate valves 112 and 115 at the closed positions because of resilient force of springs disposed therein with the communicating passage 108 and the connection between the first merged passage 114a and the turbine 106a being interrupted. As a result, only the second supercharger 109 is ope rated to supercharge the intake gas. This causes that a flow rate introduced into the turbine 109a is increased to improve the charging efficiency of the intake gas in a lower engine speed condition (first intake condition). The engine torque changes along a curved line I as shown in Figure 2. In this case, the actuator 120 is operated slimilar to the actuator 12 as shown in Figrure 1 to maintain the maximum supercharging pressure at a predetermined low value. When the engine speed is increased to reach the predetermined value, the control unit C provides the three-way solenoid valve 125 with a signal so that the three-way solenoid valve 125 takes the second position. Thus, the supercharging pressure is applied to the actuators 118 and 119 so that the gate valve 112 and 115 are released to open the communicating passage 108 and communicate the first merged passage 114a and the turbine 106a. As a result, in a higher engine speed condition, the exhaust gas is introduced into both the turbines 106a and 109a to supercharge the intake gas for thereby improving the charging efficiency (second intake condition). the engine torque changes along the curved line II as shown in Figure 2. On the other hand, the actuator 120 is operated similar to the actuator 18 to maintain the maximum supercharging pressure at the higher value. According to the illusrated embodiment, the maximum value of the supercharging pressure utilizing the waste gate valve 117a is changed in accordance with the engine speed as well as the intake condition of introduction of the intake gas is switched utilizing the turbo superchargers 106 and 109 in accordance with the engine speed. As a result, the charging efficiency can be improved in a broader range of the engine speed preventing the knocking in a lower engine speed condition by maintaining the maximum supercharging pressure at a lower value in a low engine speed condition. In a preferred control of the engine, the waste gate valve 117a is so controlled to increase the maximum supercharging pressure of the intake gas in response to the switching operation of the condition of the introduction of the intake gas by means of the first and second surperchargers 106 and 109 in order to suppress a torque shock resulting from the change in the intake condition of the intake gas. The increased value of the maximum supercharging pressure can be reduced to the usual maximum value as the engine speed is increased beyond the predetermined value at which the first intake condition is switched to the second intake condition. Referring to Figure 7, there is shown a four cylinder engine in accordance with a further preferred embodiment of the present invention. In this embodiment, a volume of the supercharger is changed in accordance with the switching operation between the fisrt and second intake condtions. In other words, the amount of the exhaust gas is changed in accordance with the engine speed. The illustrated turbo supercharger B′ is provided with two inlet pasaages 201 and 202. A gate valve 204 is provided in the inlet passage 201 for opening and closing the inlet passage 201. A bypass passage 205 is provided for bypassing the turbine 13 of the turbo supercharger B′. There is provided a waste gate valve 206 for opening and closing an upstream end portion of the bypass passage 201. In order to control the waste gate valve 206, an actuator 207 is provided. A three-way solenoid valve 208 is provided for controlling operation of the actuators 203 and 207. In operation, when the engine speed is in a lower range, the three-way solenoid valve 208 is in a position in which the actuator 203 is released to the atmosphere so that the gate valve 204 is kept at the closed position because of the resilient force of spring to close an inlet passage 201 of the turbine 13. As a result, the exhaust gas is introduced into the turbine 13 through only the inlet passage 202 to increase a flowing speed thereof so that supercharging effect of the surpercharger B′ is increased to improve the charging efficiency in the lower engine speed condition. When the engine speed is increased to reach a predetermined value, the three-way solenoid 208 receives a control signal from the control unit C to take the second position in which the supercharging pressure is introduced into the actuator 203. When the force caused by the supercharging pressure overcomes the resilient force of the spring in the actuator 203, the gate valve 204 is operated to be opened. As a result, the exhaust gas is introduced into the tubine 13 through not only the inlet passage 201 but also the inlet passage 202 in the higher engine speed condition. That is, the amount of the exhaust gas introduced into the turbine 13 is increased to raise the output of the supercharger B′ so that the charging efficiency of the intake gas is improved in the higher engine speed condition. In this case, On starting the introduction of the surpercharged gas into the actuator 203, the supercharging pressure is introduced into the actuator 207 through the three-way solenoid valve 208 so that opening rate of the waste gate valve 206 is controlled to change the maximum supercharging pressure of the supercharger B7 from a lower value to a higher value. The operation of the actuator 207 of the waste valve is similar to that of the actuator 18 in Figure 1. According to the illustated embodiment of the invention, the switching of the intake condition of the intake gas is carried out in response to the change of the maximum supercharging pressure controlled based on the opening of the waste gate valve 206 so that the charging efficiency of the intake gas is accomplished in the broader range of the engine speed with suppressing the knocking in the lower engine speed condition.

Claims: A control system for an engine having only a turbo supercharger (B) comprising first switching means (6) for switching an introduction of intake gas to the engine in accordance with engine speed at a threshold speed (N) between a first intake condition (I) in which a charging efficiency of the intake gas is improved in a lower engine speed condition (N₀<n<N) and a second intake condition (II) in which the charging efficiency is improved in a higher engine speed condition (n>N), and second switching means (16) for switching a maximum supercharging pressure of the turbo supercharger from a lower pressure (P₁) to a higher pressure (P₂) when the first intake condition (I) is switched to the second intake condition (II), said first switching means (6) being formed by a variable valve (6) in the intake system and said second switching means (16) comprising a waste gate valve (16) for controlling the introduction of exhaust gas to a turbine of said turbo supercharger (B). A control system for an engine having two turbo superchargers (B) comprising first switching means (6) for switching an introduction of intake gas to the engine in accordance with engine speed at a threshold speed (N) between a first intake condition (I) in which a charging efficiency of the intake gas is improved in a lower engine speed condition (N₀<n<N) and a second intake condition (II) in which the charging efficiency is improved in a higher engine speed condition (n>N), second switching means (16) for switching a maximum supercharging pressure of the second turbo supercharger from a lower pressure (P₁) to a higher pressure (P₂) when the first intake condition (I) is switched to the second intake condition (II), and third switching means for rendering the first turbocharger inoperative in the first intake condition and operative at the higher pressure in the second intake condition, said first switching means (6) being formed by a variable valve (6) in the intake system and said second switching means (16) comprising a waste gate valve (16) for controlling the introduction of exhaust gas to the turbines of said turbo supercharger (B). A control system as recited in claim 1 or 2, wherein said variable valve (6) selectively establishes two different intake systems having different natural frequency exerting resonance effects in different engine speed ranges. A control system as recited in claim 3, wherein said variable valve (6) comprises gate valve means for switching the intake systems. A control system as recited in claim 3, wherein said variable valve establishes the two different intake systems by changing a length of intake passage through which the intake gas is introduced into the engine. A control system as recited in claim 1, wherein said first switching means is constituted by valve timing control means (30) for changing an opening and closing timing of the intake valve. A control system as recited in claim 1, wherein said second switching means comprises said waste gate valve (16) and actuator means (18, 19a, 20) connected with the waste gate valve (16) for controlling an operation of the waste gate valve. A control system as recited in claim 7, wherein the actuator means (18) comprises a large cylindrical portion (18a) and a small cylindrical portion (18b) partitioned by large and small diaphragms (19a, 19b) to define first and second large chambers (18a₁, 18a₂) and first and second small chambers (18b₁, 18b₂) respectively, a spring (20) disposed in the first large chamber (18a₁) for urging the large diaphragm (19a) towards the second large chamber (18a₂), a rod (17) connected to the waste gate valve (16) and the large and small diaphragms, the supercharging pressure being introduced into the second large chamber (18a₂) and the first small chamber (18b₁), and the first large chamber (18a₁) and the second small chamber (18b₂) being opened to the atmosphere. A control system as recited in claim 7, wherein the actuator means further comprises a three-way valve (23) for controlling the introduction of the supercharging pressure into the second large chamber (18a₂) and the first small chamber (18b₁). A control system as recited in claim 7 wherein the supercharging pressure is introduced into only the second large chamber (18a₂) when the engine speed reaches a first predetermined value so that the waste gate valve (16) is actuated to be opened, is introduced into both the first small chamber (18b₁) and the second large chamber (18a₂) when the engine speed is increased to reach a second predetermined value from the first predetermined value so that the waste gate valve is moved towards a closed position, and the waste gate valve (16) being moved towards an opened position when the supercharging pressure is increased beyond a predetermined value because of a difference in pressure area between the small and large diaphragms. A control system as recited in claim 7, wherein the valve timing control means (30) comprises a cam shaft (31) for driving the intake valves, a sleeve (30a) of a substantially H-shaped cross section incorporated into the cam shaft, the cam shaft being provided with a first portion (31a) on which cam portions are formed and a second portion (31b) connected with a pulley (32) which is driven by a crank shaft, the first portion and second portion being formed with helical splines (33a) at one ends respectively facing each other but oriented opposite to each other, the sleeve being formed with a pair of flange portions (30a₁, 30a₂) which are formed with a threaded opening brought into engagement with the splines. A control system as recited in claim 11, wherein a relative angular relationship between the first portion (31a) and the second portion (31b) is so determined that the intake valve timing is advanced in the lower engine speed range condition. A control system as recited in claim 1, wherein the first switching means comprises both a variable valve (6) for switching a natural frequency of an intake system of the engine to tune specific engine speeds and a valve timing control means (30) for changing an opening and closing timing of the intake valve, the valve timing control means changing the introduction of the intake gas from the first intake condition to the second intake condition at an engine speed lower than an engine speed in which the variable valve (6) changes the introduction of the intake gas from the first to the second intake condition. A control system as recited in claim 1 wherein the first switching means is constituted by a volume changing device for changing a volume of the turbo supercharger.

Inventors: HITOMI MITSUO, NISHIKAWA TOSHIO, TAKEUCHI NOBUO, HITOMI, MITSUO, NISHIKAWA, TOSHIO, TAKEUCHI, NOBUO
Applicants: MAZDA MOTOR, MAZDA MOTOR CORPORATION
Application year: 1990
Main classification: F02B37
IPC codes: F02B75, F02B37, F02B33, F02B27, F01L1