Abstract:
PROBLEM TO BE SOLVED: To provide an exhaust gas recirculation device for an internal combustion engine, capable of reducing variations in the introduction amount of EGR gas of each cylinder dependent on an operation region.SOLUTION: An exhaust gas recirculation device for an internal combustion engine comprises: an EGR passage having an EGR introduction part opening to each intake passage after branching for each cylinder and connecting an exhaust passage with each intake passage; and an air flow control valve provided to each intake passage at an intake upstream side from an opening position of the EGR introduction part and the intake passage and capable of reducing an intake flow rate in the vicinity of the opening position as compared with the other portions by being closed. An opening area of the EGR introduction part and each intake passage is set to be larger in the cylinder positioned at the upstream side of the EGR passage than in the cylinder positioned at the downstream side. The opening position of the cylinder positioned at the upstream side of the EGR passage is set to be further spaced apart from the air flow control valve than that of the cylinder positioned at the downstream side. The air flow control valve is closed in a light load region, and the air flow control valve is opened in a high load region having a higher engine load than the light load region.
Abstract:
PROBLEM TO BE SOLVED: To suitably correct a fuel injection quantity when, for example, performing divided injections of fuel. SOLUTION: A fuel injection control device of an internal combustion injects fuel by dividing more than once per one cycle, and includes a correction amount specifying means (30) for specifying a correction amount (Q×(α-1)) with respect to a total fuel injection amount (Q) to be injected per one cycle based on a predetermined parameter (air-fuel ratio A/F), and a correction means (30) for performing partial correction of a fuel injection amount with respect to a part of the fuel injection divided more than once, based on the specified correction amount. COPYRIGHT: (C)2009,JPO&INPIT
Abstract:
PROBLEM TO BE SOLVED: To increase the fuel injection rate of the fuel injection valve provided in the air intake passage as the concentration of alcohol in the fuel increases, protects the cylinder fuel injection valve, and improve the operating performance of the dual injection type internal combustion engine for FFV. SOLUTION: The internal combustion engine 10 is equipped with a port injection valve 16 to inject fuel into the air intake passage 14 and a cylinder injection valve 18 to inject fuel into the cylinder 12. The ECU 40 causes either or both of fuel injection valves 16 and 18 to inject fuel according to the operating status of the internal combustion engine 10. In this case, the ECU 40 increases the port injection rate α as the concentration of alcohol Ma in the fuel is higher. This can increase the fuel consumption of the port injection valve 16 to improve fuel consumptions and torque fluctuations, and adequately inject fuel into the cylinder injection valve 18 to prevent deposition of deposits and the like. COPYRIGHT: (C)2009,JPO&INPIT
Abstract:
PROBLEM TO BE SOLVED: To provide an internal combustion engine capable of decreasing residual gas so as to prevent aggravation of combustion, occurrence of knocking, increase of fuel consumption and decrease of output and to preferably control the banks, by preventing adverse effect caused by exhaust pulsation generated in a communication passage for communicating exhaust passages of left and right banks. SOLUTION: In the V-type six cylinder engine, cylinder groups are provided in which a plurality of cylinders are arranged and divided into the left first bank 12 and the right second bank 13. An intake pipe 51, as well as a first exhaust pipe 57 and a second exhaust pipe 58, are connected to the cylinder groups of the banks 12, 13. A first upstream three-way catalyst 59 and a first control valve 64 are provided in the exhaust pipe 57 while a second upstream three-way catalyst 60 and a second control valve 65 are provided in the exhaust pipe 58. The exhaust pipes 57, 58 are communicated with each other on the upstream sides of the upstream three-way catalysts 59, 60 and the control valves 64, 65 by a communication pipe 63. A third control valve 66 for adjusting the flow rate of exhaust gas is provided in the communication pipe 63. COPYRIGHT: (C)2008,JPO&INPIT
Abstract:
PROBLEM TO BE SOLVED: To provide the high inertial supercharging effect, regardless of an operation state of a tumble control valve. SOLUTION: This intake control device has a first intake passage 5, a second intake passage 8, an intake passage length changing valve 11, a partition wall 14 forming two divided intake passages 12 and 13, and the tumble control valve 17. When closing one of the divided intake passages by the tumble control valve, air flowing in a combustion chamber via the other divided intake passage, forms a tumble flow. The length of the second intake passage is formed longer than the length up to a connecting place S of the second intake passage and the first intake passage from a surge tank. The passage cross-sectional area of the second intake passage is formed smaller than the passage cross-sectional area of the first intake passage up to the connecting place of the second intake passage and the first intake passage from the surge tank. The tumble control valve is installed on the partition wall so as to rotate around a rotary shaft installed on the partition wall. COPYRIGHT: (C)2008,JPO&INPIT
Abstract:
PROBLEM TO BE SOLVED: To improve turbo response when engine rotation speed is accelerated from a low state. SOLUTION: An ignition control device 50A of an internal combustion engine 10 with an exhaust turbo supercharger 40 for controlling respective ignition operations of a plurality of ignition plugs (first and second ignition plugs 70A, 70B) provided for one cylinder, is provided with an actuating ignition number control means 50a for reducing the number of ignition plugs which performs the ignition operation in respective ignition plugs (first and second ignition plugs 70A, 70B) at the time of acceleration when engine rotation speed is low. For instance, the actuating ignition number control means 50a ignites the first ignition plug 70A only in the first and second ignition plugs 70A, 70B. COPYRIGHT: (C)2007,JPO&INPIT
Abstract:
PROBLEM TO BE SOLVED: To provide a device and a device for controlling an internal combustion engine capable of restraining overheating a catalyst bed temperature when the internal combustion engine with a cylinder injection valve and a port injection valve is operated. SOLUTION: This device 10 for controlling an internal combustion engine controls an internal combustion engine with a port injection valve and a cylinder injection valve. The device includes a catalyst bed temperature determining part 22 determining whether the catalyst bed temperature exceeds a predetermined reference value or not based on a parameter relating to the catalyst bed temperature for purifying exhaust gas of the internal combustion engine, and an injection ratio control part 23 for increasing a fuel injection volume of the port injection valve when the catalyst bed temperature exceeds the predetermined reference value. COPYRIGHT: (C)2005,JPO&NCIPI
Abstract:
PROBLEM TO BE SOLVED: To provide a direct injection type spark ignition combustion engine in which an air-fuel mixture is stably formed and sprayed fuel is finely atomized. SOLUTION: There is provided an internal combustion engine that is equipped with a combustion chamber 3 at a cylinder head side and performs direct injection of fuel 2 to an inside of a cylinder to burn the fuel. The combustion engine includes an intake air flow deflection means 8 for deflecting the flow of the intake air 9 sucked in the cylinder to produce the flow of the intake air 9 proceeding to a fuel injection valve 1 and the fuel injection valve 1 for performing the fuel injection against the intake air 9 deflected. Since performing injection of the fuel 2 against the intake air 9, the fuel 2 is subjected to atomization to further mix with the intake air. COPYRIGHT: (C)2005,JPO&NCIPI
Abstract:
PROBLEM TO BE SOLVED: To set a compression ratio of an internal combustion engine as high as possible, and to enable stratified charge combustion also with respect to wider fluctuation of a fuel injection flow rate from a fuel injection valve, in a cylinder injection type spark ignition internal combustion engine. SOLUTION: The cylinder injection type spark ignition internal combustion engine 10 is equipped with the fuel injection valve 1 provided in an intake valve 6 side of a cylinder head 11 and injecting fuel in a central direction of a combustion chamber 9, a first ignition plug 2 provided in an approximate center of the combustion chamber 9, and a second ignition plug 3 provided in a portion of the cylinder head 11 opposing to the fuel injection valve 1. A hump part 8a corresponding to a shape of an inner wall face of the cylinder head 11 is provided for a top part of a piston 8, and a first cavity 8b and a second cavity 8c are provided on the hump part 8a opposing to the first ignition plug 2 and the hump part 8a opposing to the second ignition plug 3, respectively. COPYRIGHT: (C)2005,JPO&NCIPI
Abstract:
PROBLEM TO BE SOLVED: To assure stable combustion with a simple structure by securely scavenging the inside of a sub combustion chamber. SOLUTION: The spark ignition type internal combustion engine is provided with the sub combustion chamber 12 separated from a main combustion chamber 5, and the main combustion chamber 5 is connected to the sub combustion chamber 12 through a communication path 13. An ignition plug 14 is arranged inside the sub combustion chamber 12, and fuel-air mixture in the sub combustion chamber 12 is ignited by the ignition plug. A scavenging passage 15 for scavenging inside the sub combustion chamber 12 is connected to the auxiliary combustion chamber 12, and outflow ends of the scavenge air passage 15 are open inside a valve seat 7. When an intake valve 7 is closed, the scavenge air passage 15 is blocked by the intake valve 7. When the intake valve 7 is open, the scavenge air passage 15 is opened. At this time, remaining gas B in the sub combustion chamber 12 is sucked out through the scavenging passage 15 by vacuum occurring around the outflow ends of the scavenging passage 15 by a fresh air flow A. COPYRIGHT: (C)2004,JPO&NCIPI