SUPERCHARGING APPARATUS FOR INTERNAL COMBUSTION ENGINE

Abstract: A supercharging apparatus for an internal combustion engine comprises the screw type supercharger (1) having an inlet opening (5) and an outlet opening (18) and the supercharger is adapted to compress intake air relative to the engine (26) in compression chambers (2d) between the openings when an electromagnetic clutch (15) engages the supercharger with the crankshaft (33) of the engine. The supercharging apparatus includes an intake air bypass passage (42) for allowing the intake air to bypass the supercharger and a bypass control valve (43) provided therein for closing the passage. The supercharger has a communication passage (37) for allowing the two compression chambers (2d) to intercommunicate for relieving the compression chambers of the compression pressure therein, and a controller (41) allows the communication passage (37) to releive the compression pressure during the disengagement of the electromagnetic clutch (15) and causes the bypass control valve (43) to close the intake air bypass passage (42) in association with the relief of the compression pressure by the communication passage.

Description: This invention relates to a supercharging apparatus for an internal combustion engine according the first part of claim 1. A variety of superchargers are generally used for internal combustion engines. In recent years, screw type superchargers have been noted because they provide enhancement of the volumetric efficiency and the possibility of improving the overall adiabatic efficiency. In a case where such a type of supercharger is arranged in an air intake system of an engine and is used for compressing the intake air, it is necessary to relieve or reduce the pumping loss of the supercharger because the supercharger causes a relatively large pumping loss in low load or partial load operating conditions of the engine. Conventionally, under those circumstances, the supercharger is connected to drive means for the supercharger through an electromagnetic clutch, and the clutch is released in the conditions in which the superconducting effect is not required, so that the supercharger is not being driven. This kind of supercharger, however, has relatively large resistance to its running during its non-driven state and is difficult to idle and therefore, a torque shock due to an engagement of the electromagnetic clutch occurs as the clutch is changed from its disengagement state to the engagement state. To prevent such a torque shock, it is required to engage the clutch at a relatively low engine speed zone, even if the engine does not require to be supercharged in the low load operating condition. It follows that it is desirable to deactivate the compression action of the supercharger entirely, or to greatly relieve the compression action. If the compression action of the supercharger can be deactivated entirely or relieved greatly, advantages would be obtained. For instance, the torque shock due to the engagement of the electromagnetic clutch could be depressed and therefore, the rotating speed to engage the clutch in the low load operating condition could be enhanced. This is brought about because the supercharger can idle during its non-driven state, and the significant differences between the rotating speed thereof and the rotating speed of the drive means for the supercharger are thus avoided. In Japanese Laid-Open Publication No. 63-170524, it has been proposed that a supercharging apparatus for an internal combustion engine having both a screw type supercharger and a turbocharger be so constituted that the capacity of the screw type supercharger is reduced to decrease the pumping loss when the engine is operated in partial load conditions. That is, in this conventional supercharging apparatus, the screw type supercharger has control valves which are slideable axially and its intake air inlet is adapted to be opened by the control valves in order to reduce the capacity of the supercharger. This type of supercharger might be able to reduce the pumping loss in low load or partial load operating conditions to some extent, but there still remains the compression action thereof and therefore, since the idle rotation of supercharger is limited during its disengagement with the drive means, the torque shock occurs upon an engagement with the drive means for the supercharger owing to a considerable variation in the engine torque. A supercharging apparatus according the first part of claim 1 is known from US-A-4,527,534. This supercharger is driven from the engine crankshaft via a clutch and has a bypass passage controlled by a valve. This valve is set to a low maximum pressure when the clutch is connected and the maximum pressure then increases as the load on the engine increases. One object of the present invention is to provide a supercharging apparatus for an internal combustion engine that can prevent the engine from causing a torque shock owing to a considerable variation in the torque as a supercharger operatively engages with drive means for the supercharger. Another object of the present invention is to provide a supercharging apparatus for an internal combustion engine that can ensure that the engine applies the desired torque during a transition period in which relatively quick acceleration of the engine speed is performed and a supercharger comes into operative engagement with drive means for the supercharger. Still another object for the present invention is to provide a supercharging apparatus for an internal combustion engine that can ensure the desired flow of intake air relative to the engine in good response during a transition period in which relatively quick acceleration of the engine speed is performed but the supercharger remains held in disengagement with drive means for the supercharger. The foregoing and other objects and advantages are attained, according to the present invention, by a supercharging apparatus for an internal combustion engine comprising: a supercharger having an inlet opening and an outlet opening and being adapted to compress intake air relative to the engine in a compression area between the openings; clutch means for engaging and disengaging the supercharger with drive means for driving the supercharger; passage means for allowing the intake air to bypass said supercharger, said passage means being provided with valve means for closing the passage means; relief means for relieving at least partially the compression area of the compression pressure therein; and control means for causing said relief means to relieve the compression during the disengagement of said clutch means and controlling said valve means in association with the relief means. Preferred embodiments of the invention may have the following additional features, either alone or in combination: (1) said control means causes said valve means to close said passage means at a predetermined period of time when the engine performes an acceleration of the engine speed and said clutch means engages said supercharger with said drive means. (2) said control means causes said valve means to open said passage means at a predetermined period of time when the engine performes an acceleration of the engine speed and said clutch means holds said supercharger in disengagement with said drive means. BRIEF DESCRIPTION OF THE DRAWINGS The above and other objects, advantages and novel features of the present invention will be made more fully apparent from a reading of the following detailed descriptions taken in conjunction with the accompanying drawings in which; Figure 1 is a semi-schematic, perspective view showing an embodiment of a supercharger in accordance with the present invention. Figure 2 is a vertical cross-sectional view of the supercharger device shown in Figure 1. Figure 3 is a transverse cross-sectional view of the supercharger device shown in Figure 1. Figure 4 is a schematic view showing an air intake system of an engine which is provided with the supercharging apparatus in accordance with the present invention. Figure 5 is a graphical representation showing an illustrative zoning of operating condition of the engine for controlling opening and closing of a communication passage of the supercharger and operation of an electromagnetic clutch of the supercharger. Figure 6 is a semi-schematic enlarged cross-sectional view showing an arrangement of the communication passage and a valve provided thereon in the supercharger. Figure 7 is a graphical representation showing a manner of controlling a bypass control valve provided in a bypass passage. Figure 7A is a graphical representation showing an alternative manner of controlling the bypass control valve. Figure 8 is a flow chart partially showing the operation of a controller shown in Figure 4. Figure 9 is a flow chart showing the other part of the operation of the controller. DESCRIPTION OF THE PREFERRED EMBODIMENT With reference to Figures 1 through 3, there is illustrated a supercharger constituting a supercharging apparatus for an automotive internal combustion engine in accordance with one embodiment of the present invention. The supercharger 1 has a pair of female and male rotors 3, 4, which are disposed in a housing 2. The rotor 3 is provided with helical grooves 3a thereon, and the rotor 4 is provided with helical lobes 4a thereon. These rotors 3,4 are positioned in parallel with each other, and the grooves 3a of the rotor 3 intermesh with the lobes 4a of the rotor 4 as shown in Figure 3. The housing 2 is constituted of a central housing 2a and end housings 2b, 2c which are secured to respective ends of the central housing 2a. As best shown in Figure 3, the rotors 3, 4 define a plurality of compression chambers 2d in cooperation with the housing 2, which constitute a compression area and are rotated as shown by arrows. As shown in Figure 2, the end housing 2b is formed with an intake air inlet opening 5 which opens axially. A bearing plate 6 is secured to the end housing 2c and an end plate 7 is fixed to the bearing plate 6. The rotors 3, 4 have shafts 3b, 4b respectively, which are rotatably mounted on bearings 8 disposed on the end housing 2b at one end portions and are rotatably mounted on sleeve bearings 9a, 9b disposed on the end housing 2c and bearings 10 disposed on the bearing plate 6 at the other end portions. The shafts 3b, 4b of the rotors 3, 4 are provided with intermeshing gears 3c, 4c. A shaft 13 is mounted on the end plate 7 by means of bearings 11, 12 and is concentric with the shaft 3b of the rotor 3. A pulley 14 is disposed on the shaft 13, and this pulley 14 is disengagably connected to the shaft 13 through an electromagnetic clutch 15, which is provided on the shaft 13. The shaft 13 has a gear 16, which meshes with a gear 17 on the shaft 4b of the rotor 4. The central housing 2a is formed with an intake air outlet opening 18 at its end portion close to the end housing 2c. Figure 4 illustrates a supercharging apparatus which uses the supercharger 1 shown in Figures 1 through 3. With reference to Figure 4, the intake air inlet opening 5 is connected to an upstream intake air passage 19 and the intake air outlet opening 18 is connected to a downstream intake air passage 20. In the upstream intake air passage 19, there is disposed an air cleaner 21, an airflow meter 22 and a throttle valve 23, in succession from the upstream side. The downstream intake air passage 20 is provided with an inter cooler 20 and is formed with a surge tank 25 at its downstream end portion. An engine 26 has a cylinder block 27 formed with cylinder bores 27a and a cylinder head 28 mounted on top of the cylinder block 27. A piston 29 is provided in each of the cylinder bores 27 and in slicing contact with an inside wall of the bore, that is, a cylinder wall 27a. The surge tank 25 is in communication with each of combustion chambers 31 defined within the respective cylinder bores 27, through an intake manifold 30 and an intake valve or valves. Connecting rods 32 are attached at one end to the pistons 29 and at the other end to a crank pin (not shown) of a crankshaft 33. A pulley 34 secured to the crankshaft 33 is operatively connected with the pulley 14 on the shaft 13 of the supercharger 1 by means of an endless belt 35. With this arrangement, the crankshaft 33 of the engine 26 drives the rotors 3, 4 of the supercharger 1 to rotate them, during engagement of the electromagnetic clutch 15. When the rotors 3, 4 of the supercharger 1 are driven to rotate, the rotation of the rotors 3, 4 allows the compression chambers 2d defined in the housing 2 to displace circumferentially with respect to the housing, and therefore, the volume of the chamber 2d gradually reduces with the rotation of the rotors 3, 4 so that the intake air therein is compressed. The area 36 as shown with shadow lines in Figures 2 and 3, is a discharge area of the pressurized air, that is, supercharged air, and this discharge area 36 is in communication with the intake air outlet opening 18. Accordingly, in the usual operation of the supercharger 1, the intake air introduced thereinto through the intake air inlet opening 5 is compressed before reaching the discharge area 36, and is delivered through the air intake outlet opening 18 to the downstream intake passage 20. Figure 5 shows the relationship between the control of engagement and disengagement of the electromagnetic clutch 15 and the operating condition of the engine. In Figure 5, the zone A is an engine operating zone in which the opening of the throttle valve 23, namely, throttle opening T, is smaller than a predetermined value T₀ and the engine speed N is lower than a predetermined speed N₀, that is, the engine 26 operates under unload or low load conditions. When the engine 26 operates within the zone A, the electromagnetic clutch 15 is disengaged or released so that the rotors 3, 4 can rotate freely. There is provided means for depressing or relieving the compressing action of the supercharger 1 under the operating conditions within the zone A so that the running resistance therein is reduced. This means comprises a communication passage 37 formed in the end housing 2c and a valve 38 as best shown in Figure 6. As shown in Figure 3, the communication passage 37 is formed in a position which allows, the two compression chambers 2d to intercommunicate on an upstream side of the discharge area 36. Preferably, the communication passage 37 may be provided so that the passage 37 can continue the above intercommunication us to immediately before the compression chamber 2d in advance reaches the discharge area 36. Referring to Figure 6, the communication passage 37 is provided with a valve seat 37a at one end there of facing to the rotor 3, and the valve 38 is abutted against the valve seat 37a from the outside of the end housing 2c. A valve spring 39 biases the valve 38 toward the valve seat 37a, so that the valve 38 is kept closed. A solenoid 40 is provided for shifting the valve 38 to open it. In order to control the solenoid 40 and the electromagnetic clutch 15, there is provided a controller 41 as shown in Figure 4. This controller 41 receives, as input signals, an engine speed signal N, an intake air volume signal Q and a throttle valve position signal indicating the throttle opening T and the angular velocity d ϑ /dt of the throttle valve 23, respectively, and on the basis of these signals, the controller 41 discerns whether the present operating condition of the engine 26 is in the zone A as shown in Figure 5. When the controller 41 discerns that the present operating condition of the engine is in the zone A, it energizes the electromagnetic clutch 15 to disengage or deactivate the clutch 15 by a clutch control signal. Further, when the controller 41 discerns that the present throttle T is not more than the predetermined opening value T₁, it energizes the, solenoid 40 by a communication passage control signal to shift the valve 38 into its open position so that the communication passage 37 is released. The value T₁ is indicated in Figure 5, which is set larger than the value T₀ so as not to duplicate the timimg of engaging the electromagnetic clntch 15 and the timing of shifting the valve 38. As the communication passage 37 is released, the two compression chambers 2d come into intercommunication, and the air to be compressed within the chamber 2d in advance as seen on left side of the communication passage 37 in Figure 3, flows out into the other chamber 2d in retard as seen on right side of the communication passage 37. Therefore, the pressure of the air in the former chamber 2d is reduced to relieve the compressing action. Referring to Figure 4, there is provided a bypass passage 42, one end of which is connected to the upstream intake air passage 19 downstream of the throttle valve 23 and the other end of which is connected to the downstream intake air passage 20 downstream of the inter cooler 24. A bypass control valve 43 is disposed in the bypass passage 42, and a pneumatic actuator 44 is connected with a valve stem of the control valve 43 for operating the control valve 43. Into the actuator 44, the pressure in the upstream intake air passage 19 downstream of the throttle valve 23 can be introduced through a conduit 45, in which a solenoid-operated three-way control valve 46 is interposed. When the three-way control valve 46 takes a position in which the valve 46 allows the actuatar 44 to be in communication with the upstream intake air passage 19, the pressure in the passage 19 is introduced into the actuator 44. In this situation, provided that the pressure is lower than a predetermined value, the actuator 44 allows the bypass control valve 43 to open the bypass passage 42. The three-way control valve 46 can take a position in which it allows the actuator 44 to release to the atmosphere, wherein the actuator 44 holds the bypass control valve 43 in its close position. As shown in Figure 4, the output of the controller 41, that is, a bypass passage control signal is also applied to the three-way control valve 46, so that the valve 46 is controlled in its position by the controller 41. As best shown in Figure 7, the three-way control valve 46 is released to the atmosphere and the bypass control valve 43 is closed, under an operating condition in which the throttle opening T and the engine speed N (rpm) are smaller than the predetermined values T₀ and N₀ respectively. On the other hand, under the operating condition in which the throttle opening T is larger than the value T₀, the three-way control valve 46 causes the upstream intake air passage 19 to come into communication with the actuator 44, so that the opening of the bypass control valve 43 is under the control of the pressure of the intake air in the intake air passage 19. Figure 8 shows the steps for controlling the electromagnetic clutch 15, the three-way control valve 46 and the solenoid 40. At the first step, the controller 41 reads the present engine speed N and the throttle opening T of the throttle valve 32. Then, on the basis of the read information, the controller 41 discerns whether the engine 26 operates in the engine operating zone to engage the electromagnetic clutch 15, namely out of the zone A as designated in Figure 5. If the engine 26 operates out of the zone A, the electromagnetic clutch 15 is deenergized to come into engagement, as well as a flag F₀ is set into "1". When the engine 26 operates in the zone A, the electromagnetic clutch 15 is energized to be in disengagement, as well as the flag F₀ is set into "0". Then, the position of the flag F₀ is read for controlling the three-way control valve 46, and so long as the flag F₀ is positioned in "1", the valve 46 is energized to shift into the position which causes the upstream intake air passage 19 and the actuator 44 to intercommunicate As a result, the opening of the bypass control valve 43 is under the control of the pressure in the intake air passage 19. Conversely, if the flag F₀ is "0", the three-way control valve 46 is deenergized to be kept closed. After that, the controller 41 discerns on the basis of the throttle opening T, whether the engine 26 operates in the engine operating zone B to open the communication passage 37 in the supercharger 1, that is, whether the throttle opening T is not more than the predetermined value T₁. Provided that the engine 26 operates in the zone B, that is, the opening T is not more than the value T₁, the solenoid 40 is energized to open the communication passage 37. On the other hand, if the engine 26 operates out of the zone B, that is, the opening T is more than the value T₁, the solenoid 40 is deenergized to close the communication passage 37. Under this control, the intake air passes through the supercharger 1 during the operation of the engine not to drive the supercharger 1, so that the flow of the intake air through the supercharger 1 is increased, in comparison with a case where the the bypass passage would be opened at this time. Further, the supercharger 1 is relieved of its compression action, so that the resistance relative to its idle rotation is greatly lowered. Therefore, the supercharger 1 is substantially freely rotated by the intake air flowing therethrough, and when the electromagnetic clutch 15 is engaged again, the differences between the rotating speed of the supercharger 1 and the one of the crankshaft 33 of the engine 26 have been reduced. Thus, upon re-engagement of the electromagnetic clutch 15, it is possible to prevent the engine 26 from causing so-called torque shock involved in a rapid reduction of the engine torque. Figure 9 shows a manner of control during acceleration. At the first step, the controller 41 reads the position of the flag F₀ and the angular velocity dϑ/dt of the throttle valve 23, which corresponds to a driver's push-down operation relative to an accelerator pedal (not shown). Then, the controller 41 discerns whether or not the velocity dϑ/dt is more than a predetermined value C. If the velocity dϑ/dt is more than the value C, the controller 41 further reads the position of the flag F₀. When the flag F₀ is positioned in "1", the controller set Flag F₁ into "1" and times a timer TM to terminate at the count ΔTM₁. Further, the controller 41 deenergizes the three-way control valve 46 to keep the bypass control valve 43 in its close position until the timed term ΔTM₁ expires. Such a manner of control is carried out, in a case where the throttle opening T presents a considerable rapid variation upwardly from the zone A to disengage the electromagnetic clutch 15 to the zone B to engage the clutch 15 as shown by an arrow D in Figure because of a quick push-down operation on the accelerator pedal. In this case, as set forth above, the controller 41 discerns the situation of the engine 26 on the basis of the throttle opening T after the push-down operation on the accelerator pedal and the angular velocity d ϑ /dt corresponding to the movement of the accelerator pedal during the operation, and carries out the control relative to the bypass control valve 43 to keep the valve 43 in its close position at the preset period ΔTM₁. Such a control allows the flow of the intake air through the supercharger 1 to increase upon a quick acceleration, so that the output torque of the engine 26 can be enhanced. When the flag F₀ is not positioned in "1", the controller 41 energizes the three-way control valve 46 so that the valve 46 causes the upstream intake air passage 19 to communicate with the actuator 44 for opening the bypass control valve 43, after setting a flag F₂ into "1" and timing the timer TM to terminate at the count ΔTm₂. Such a manner of control is carried out, in a case where an acceleration is effected to the extent that the throttle opening T does not exceed the zone A to disengage the electromagnetic clutch 15 and therefore, the throttle opening T remains in the zone A. In this case, as apparent from the above description, the bypass control valve is forced to be opened at the preset period ΔTm₂, even if the opening T is in the zone A. Such a control allows the flow of the intake air for the acceleration to be supplied to the engine 26 through the bypass passage 42, and thus, this can prevent the engine 26 from retarding the acceleration. After the push-down operation of the accelerator pedal is accomplished, the angular velocity d ϑ /dt usually becomes lower than the value C. In this situaiton, the controller 41 discerns the position of the flag F₁ and, if the flag F₁ resides in "1" and the counts of the timer TM is past the preset period ΔTM₁, the controller 41 deenergizes the three-way valve 46 so that the bypass control valve 43 is closed. Further, the controller 41 initializes the flag F₁ to "0". If the flag F₁ resides in "0", the controller 41 discerns the position of the flag F₂ and, provided that the flag F₂ resides in "1", energizes the three-way control valve 46 so that the bypass control valve 43 is opened until the counts of the timer TM is past the preset period ΔTm₂. Further, the controller 41 initializes the flag F₂ to "0" and thus completes its control relative to the control valves 43, 46. As described above with reference to the prefered embodiments, according to tee present invention, the supercharging apparatus for the internal combustion engine 26 can be provided, which comprises the supercharger 1 having the inlet opening 5 and the outlet opening 18 and being adapted to compress the intake air relative to the engine 26 in the compression chambers 2d between the openings, the electromagnetic clutch 15 for engaging and disengaging the supercharger 1 with the crankshaft 33 of the engine 26, the intake air bypass passage 42 for allowing the intake air to bypass the supercharger 1, a bypass control valve 43 provided therein for closing the passage 42, the communication passage 37 for allowing the two compressing chambers 2d to intercommunicate for relieving the compressing chambers 2d of the compression pressure therein, and controller 41 for causing the communication passage 37 to relieive the compression pressure during the disengagement of the electromagnetic clutch 15 and causing the bypass control valve 43 to close the intake air bypass passage 42 in association with the relief of the compression pressure by the communication passage 37. With this arrangement, the compression pressure is relieved in the operating conditions of the enigne 26 in which the supercharger 1 is disengaged with the crankshaft 33 of the engine 26 by the electromagnetic clutch 15. It follows that the supercharger 1 is easy to idle in those conditions. Further, the bypass control valve 43 is closed in a certain period or over the period when the supercharger 1 is disengaged with the crankshaft 33 in conjunction with the relief of the compression pressure, so that all of the intake air to be supplied to the engine 26 through the supercharger 1 in that period and therefore, the flow of the intake air for idly running the supercharger 1 can be increased. Thus, the differences between the rotaing speed of supercharger 1 and the one of the engine 26 can be reduced, and this can pevent the engine 26 from causing the considerable variation of the torque, that is, the torque shock, upon the engagement of the electromagnetic clutch 15. Further, according to the above embodiment, the bypass control valve 43 is operated to close the intake air bypass passage 42 at a predetermined period of time, when the engine 26 performes an acceleration of the engine speed and the electromagnetic clutch 15 engages the supercharger 1 with the crankshaft 33. Therefore, under such conditions, it is possible to increase the flow of the intake air through the supercharger 1 so that the supercharger 1 can attain the desired supercharging for the engine 26 to develop the required torque. Still further, the bypass control valve 43 is operated to open the intake air bypass passage 42 at a predetermined period of time, when the engine 26 performes an acceleration of the engine speed and the electromagnetic clutch 15 holds the supercharger 1 in disengagement with the crankshaft 33. This allows the intake air required for the acceleration to be supplied to the engine 26 through the bypass passage 42, and this ensures the desired acceleration of the engine 26. Figure 7A illustrates an alternative manner of controlling the bypass control valve 43. In this paticular application, the bypass control valve 43 is closed in a certain period of the throttle opening T , immediately before the throttle opening T reaches the value T₀, in other words, so long as the throttle opening T exceeds the predetermined valueT 2 and still remains below the value T₀. With this arrangement, the flow of intake air passing through the bypass passage 42 is more than the first embodiment as described above under the low load operating conditions of the engine 26 and therefore, it is possible to minimize the work which is done for idly running the supercharger 1 to reduce the differences between the rotating speed thereof and the one of the crankshaft 33. In the above enbodiments, the supercharging apparatus uses a screw type supercharger, but the supercharging apparatus may use a rootes type supercharger.

Claims: A supercharging apparatus for an internal combustion engine which is driven from the crankshaft of the engine comprising: a supercharger (1) having an inlet opening (5) and an outlet opening (18) and being adapted to compress intake air relative to the engine in a compression area between the openings; clutch means (15) for engaging and disengaging the supercharger (1) with drive means for driving the supercharger; passage means (42) for allowing the intake air to bypass said supercharger (1), said passage means being provided with valve means (43) for closing the passage means (42); characterized in relief means (37) for relieving at least partially the compression area of the compression pressure therein; and control means for causing said relief means (37) to relieve the compression during the disengagement of said clutch means and controlling said valve means (43) in association with the relief means (37). An apparatus according to claim 1, wherein said control means (41) causes said valve means (43) to close said passage means (42) while causing said relief means (37) to relieve the compression area of the compression pressure therein. An apparatus according to claim 1, wherein said control means (41) allows said valve means (43) to close said passage means (42) in a period before said clutch means (15) causes said supercharger (1) to engage with the drive means. An apparatus according to claim 2, wherein said control means (41) allows said valve means (43) to close said passage means (42) provided that the engine speed is smaller than a predetermined engine speed and allows said valve means (43) to open said passage means (42) provided that the engine speed is larger than the predetermined engine speed. An apparatus according to claim 1, wherein said control means (41) causes said valve means (43) to close said passage means (42) at a predetermined period of time, when the engine (26) performes an acceleration of the engine speed and said clutch means (15) engages said supercharger (1) with said drive means. An apparatus according to claim 1, wherein said control means (41) causes said valve means (43) to open said passage means (42) at a predetermined period of time, when the engine (26) performes an acceleration of the engine speed and said clutch means (15) holds said supercharger (1) in disengagement with said drive means. An apparatus according to claim 1, wherein said control means (41) causes said valve means (43) to close said passage means (42) at a predetermined period of time, when the engine (26) performes an acceleration of the engine speed and said clutch means (15) engages said supercharger (1) with said drive means, and said control means (41) causes said valve means (43) to open said passage means (42) at a predetermined period of time, when the engine (26) performes an acceleration of the engine speed and said clutch means (15) holds said supercharger (1) in disengagement with said drive means. An apparatus according to claim 1, wherein said clutch means (15) is adapted to cause said supercharger (1) to disengage with the drive means on the basis of the throttle opening and the engine speed of the engine (26), and said control means (41) causes said relief means (37) to relieve the compression in dependence on the throttle opening. An apparatus according to claim 8, wherein said control means (41) causes said relief means (37) to relieve the compression when the throttle opening is larger than a predetermined value, the predetermined value being set larger than a predetermined throttle opening at which said clutch means (15) causes said supercharger (1) to disengage with the drive means. An apparatus according to claim 1, wherein said supercharger (1) comprises a screw supercharger having intermeshing herical rotors on parallel axes and mounted on a housing (2). An apparatus according to claim 10, wherein said compression area includes a plurality of compression chambers (2d) separated to each other and said relief means (37) allows the two compression chambers (2a) to intercommunicate. An apparatus according to claim 11, wherein said relief means (37) comprises communication passage means which allows the compression chambers (2d) to intercommunicate when the compression chambers (2d) do not communicate with the outlet opening (18) of the supercharger (1). An apparatus according to claim 12, wherein said communication passage means (37) is provided with a passage disposed to allow the compression chambers (2d) to intercommunicate and valve means (37a, 38) for opening and closing the passage. An apparatus according to claim 13, wherein said valve means has a spring biased valve (38) disposed in the passage (37) and a solenoid (40) for shifting the valve (38) to open the passage (37). An apparatus according to claim 13, wherein said passage (37) is formed in an end housing of said supercharger (1). An apparatus according to claim 1, wherein said passage means comprises a bypass passage (42) which is connected at its ends to an air intake passage communicating with said outlet (18) and inlet (5) openings of the supercharger (1) respectively. An apparatus according to claim 16, wherein said valve means comprises a valve (43) and a pneumatic actuator (44) operatively connected thereto, the actuator (44) communicating with said air intake passage (19) through a passage (45) and a means (46) for closing the passage. An apparatus according to claim 17, wherein said actuator (44) is adapted to displace said valve (43) under control of the pressure in said air intake passage (19).

Inventors: FUJIMOTO, HIDEFUMI, IWATA, NORIYUKI, SASAKI, JUNSOU
Applicants: MAZDA MOTOR CORPORATION
Application year: 1990
Main classification: F02B33
IPC codes: F02B39, F04C28, F02B33, F04C18