Abstract:
PURPOSE:To improve combustion performance by installing a fuel injection valve into one among three intake passages and opening the suction valve in each intake passage at a specific timing and permitting stratification by properly controlling the fuel injection completion timing of the fuel injection valve. CONSTITUTION:The first and the second intake passages 12 and 13 having a relatively large sectional area and the third intake passage 4 which has a relatively small sectional area and is positioned between the both passages 12 and 13 are formed into a cylinder head 4, and the first-third suction valves 7-9 are installed into the passages 12-14, respectively. An intake control valve 19 which is opened in high load operation is installed into the second intake passage 13, and a fuel injection valve 21 is arranged onto the upper wall surface in the third intake passage 14. The first and the second suction valves 7 and 8 are opened from the vicinity of the top dead center in suction cycle to the beginning of compression cycle, and the third suction valve 9 is opened from the vicinity of the center in suction cycle to the beginning of compression cycle, and the injection completion time of the fuel injection valve 21 is controlled so as to gradually advance toward the beginning of suction cycle from the end of suction cycle, as the engine revolution speed increases.
Abstract:
PURPOSE:To improve combustion performance by achieving stratification by installing a fuel injection valve into one among two intake passages and opening a suction valve in the intake passage from the vicinity of the center of suction cycle to the beginning of compression cycle and properly controlling the fuel injection completion timing. CONSTITUTION:The first and the second intake passages 10 and 11 are formed into a cylinder head 4, and converged inside an intake branched pipe 14. The first intake passage 10 has the sectional area larger than that of the second intake passage 11, and is formed into helical form, and the second intake passage 11 is formed as straight port, and a fuel injection valve 5 is arranged onto the upper wall surface. The first intake valve 7 in the first intake passage 10 opened from the vicinity of the top dead center in suction cycle to the beginning of compression cycle, and the second suction valve 8 in the second intake passage 11 is opened from the vicinity of the center in suction cycle to the beginning of compression cycle, and the injection completion time of the fuel injection valve 15 is controlled so as to gradually advance toward the beginning of suction cycle from the end of suction cycle, as the engine revolution speed increases.
Abstract:
PURPOSE:To improve ignitability and exhaust capacity ever so better, by making the injection completion timing of a fuel injection value installed in each suction port in time of opening a control valve, to be the earlier the higher in an engine speed, in case of a engine which installs two suction valve in one cylinder and also installs the control valve in the suction port for a high speed suction valve. CONSTITUTION:Two suction valves 4 and 7 are installed in a cylinder 2 having a spark plug at the center, and a suction control valve 12 to be opened in time of high speed is installed in a suction port 8 of a high-speed suction valve 7 having such valve timing as being suitable for high speed use. At each of these low- and high-speed suction ports 5 and 8, there are provided with first and second fuel injection valves 6 and 9, whereby the controlled quantity of fuel is sprayed out of both these injection valves at all times. In time of opening the suction control valve 12, when engine speed or engine load comes high, fuel injection timing is quickened in a proportionate manner. As a result, fuel is fed to a combustion chamber from each suction passage from the outset of a suction stroke so that a rich air-fuel mixture to be formed in and around a spark plug 3 becomes somewhat rarefied.
Abstract:
PURPOSE: To suck satisfactorily fuel. CONSTITUTION: A suction port 9 is bent in a position eccentric to the rotary center line C of a rotor and provided with an introducting hole 24 extending from the outer peripheral surface of the rotor facing a peripheral groove like fuel supply port 6a to a bent part 23 and an exhaust hole 25 extending from the bent part to a fuel suction path 8. An open port part 26 of the introducing hole 24 communicating to the fuel supply port 6a on the outer peripheral surface 4a of the rotor is opened toward the rotary direction side of the rotor slong a tangent T to the outer peripheral surface 4a on the open port part 26. A force for separating suction fuel in the suction port 9 radially from the rotary center line C by a centrifugal force accompanying the rotation of the rotor acts on the suction fuel, while since the suction port has the bent part 23, the inner surface of the bent part particularly resists against the centrifugal force and only the component of the centrifugal force acts on the suction fuel. When the open port part 26 collides with the fuel in the fuel supply port 6a along with the rotation of the rotor, the fuel in the fuel supply port 6a gets liable to be sucked into the open port part 26 by a reaction force to the component of the rotary force.
Abstract:
PURPOSE:To precisely control EGR to a high-load area by calculating the indication opening of an exhaust gas re-circulating valve based on the intake pipe pressure or intake air quantity and engine rotating speed, and correcting the throttle opening accordingly when it is the preset value or above. CONSTITUTION:An arithmetic means D calculates the indication opening STEP of an exhaust gas re-circulating (EGR) valve based on the intake pressure PM or intake air quantity Q detected by the first sensor A and the engine rotating speed NE detected by the second sensor B. When the throttle opening TA detected by the third sensor C is the preset value or above, i.e., in a high-load area, the indication opening STEP is corrected by a correcting means E according to the throttle opening TA, and a control means F adjusts the opening of the EGR valve with the corrected indication opening ESTEP. EGR can be precisely controlled to a high-load area without deteriorating driveability.
Abstract:
PURPOSE:To perform an optimum lean burn control especially even in high load range at the throttle opening over a prescribed value by correcting an air-fuel ratio correcting factor based on the running condition of an internal combustion engine at least with a correcting value based on the throttle opening. CONSTITUTION:Either the intake pipe pressure or the intake air quantity of an internal combustion engine is detected with a first sensor A, and the engine speed is detected with a second sensor B. The fuel injection time decided from respective outputs of respective sensors A,B is corrected with the air-fuel ratio correcting factor institute based on the outputs of the respective sensors A,B, and lean burn control is performed by a control means C. In the above stated device, the opening of a throttle valve is detected with a throttle sensor D. When the detected throttle opening is over a prescribed value, the above stated air-fuel ratio correcting factor is corrected at least by a correcting means E based on the correcting value instituted with the throttle opening.
Abstract:
PURPOSE:To improve the firing performance by providing two more intake valves than that facing against an intake path associated with a gate valve then providing a fuel injection valve to one of said two intake valves and fixing the fuel injection finishing time thereof to a predetermined time prior to the closure of the intake valve. CONSTITUTION:First intake valve 7 and a gate valve 19 are provided to an intake port 12 for performing normal intake, while second intake valve 8 for an intake port 13 which opens the gate valve 19 under heavy load of engine so as to intake the air and a third intake valve 9 for an intake port 14 having a fuel injection valve 21 and performs normal intake are provided for each cylinder. The fuel injection starting time is controlled corresponding to the fuel injection quantity such that the finishing time of fuel injection from the fuel injection valve will be at a predetermined time point in the open interval of the third intake valve 9 irrespective of the operating condition of engine.
Abstract:
PURPOSE: To prevent adhesion of an oil film to a throttle valve by opening a blowby gas reflux tube to a gas flow passage formed between an inner tube and a downstream side intake inner tube located on its outer side. CONSTITUTION: A gas flow passage 22 is formed circumferentially between an outer periphery of an inner tube 41 and a surge tank inner wall 2a. A blowby gas circulation pipe 5 is opened to a lowermost wall end of a surge tank 2, being faced to the gas flow passage 22. The gas flow passage 22 is separated from a downstream area of a throttle valve 3 where spiral flow is generated, by a cylindrical wall of the inner tube 41, so that blowby gas passing the flow passage 22 is not influenced by the spiral flow. In addition, high speed intake flow directed to a downstream side exists near an opening 221 of the gas flow passage 22, so that the blowby gas in the flow passage 22 is suctioned by the ejector effect of the intake flow, and fed back into the surge tank 2. It is thus possible to prevent contraflow of the blowby gas to the throttle valve 3, and generation of deposite.
Abstract:
PURPOSE:To provide a control device for a multicylinder internal combustion engine whereby correction between cylinders is performed with an engine control parameter of the specific cylinder serving as a reference, relating to a device for controlling the control parameter of the engine so that a torque fluctuation amount obtains a target value after performing the correction between the cylinders. CONSTITUTION:In a control device for a multicylinder internal combustion engine 10 having an inter-cylinder correction coefficient calculating means 11, a torque fluctuation correction coefficient calculating means 12 and a control means 13, the intercylinder correction coefficient calculating means 11 calculates an intercylinder correction coefficient of each cylinder with an engine control parameter of the predetermined cylinder serving as a reference.
Abstract:
PURPOSE:To enable compensation of hysteresis characteristic by providing a means for storing variation of effective area of an EGR valve which is modified corresponding to variation of control signal for a back pressure type EGR valve and determining a control signal based on the stored information and an operating state. CONSTITUTION:In an EGR controller, a diaphragm type valve DB is arranged in an exhaust gas recirculation path CI coupling between exhaust system EX and suction system IN of an internal-combustion engine EG. A back pressure control machinery BA is controlled based on a control signal CS obtained corresponding to the operating state of the internal-combustion engine so as to control effective area of the exhaust gas recirculation path CI. Means C1 for storing variation of effective area of the valve DB to be modified corresponding to variation of the control signal CS is provided. The control signal CS to be provided to the back pressure control machinery BA is determined through a control signal determining means C2 based on the information stored in the memory means C1 and the operating state of the internal-combustion engine.