Examples are directed to a fuel injection device positioned in a cylinder liner. In one example, a cylinder includes a combustion chamber which is jointly formed by a piston crown of a piston, by a cylinder barrel which laterally delimits the combustion chamber, and by a cylinder head. The cylinder includes an injection device positioned in the cylinder barrel for direct introduction of fuel into the combustion chamber, which injection device has at least one opening which, during a course of an injection process, is configured to be activated to introduce fuel into the combustion chamber, the injection device terminating flush, at a combustion chamber side, with the cylinder barrel.

A method of assisting ignition of a dedicated exhaust gas recirculation (D-EGR) cylinder in a spark-ignited internal combustion engine. The spark igniter has an internal air passage that receives pressurized air and carries the pressurized air down to an exit port in the vicinity of the spark gap of the igniter.

A fuel injector includes an injector body with a fuel chamber configured to receive fuel from a fuel line, an injector tip provided at an end of the injector body, and one or more nozzle assemblies provided in the injector tip. The one or more nozzle assemblies have a fuel channel in fluid communication with the fuel chamber, a premixing tube fluidly connected to the fuel channel, and a port fluidly connected to the premixing tube. The premixing tube has an orifice providing an outlet for the injector tip.

Among multiple scavenging passages 14 included in a cylinder, a scavenging passage connected to at least one scavenging port 16 constitutes a variable scavenging passage 14(ch). An upper end portion of the variable scavenging passage 14(ch) has a guide surface 50 defining a discharge direction of a scavenging gas discharged from a variable scavenging port 16(ch) connected thereto on a horizontal plane. The guide surface 50 includes at least a first guide portion 50(H) defining a first discharge direction of the scavenging gas and a second guide portion 50(L) defining a second discharge direction of the scavenging gas. The discharge direction of the scavenging gas is changed from the first discharge direction to the second discharge direction on the horizontal plane by the first and second guide portions 50(H) and 50(L) in the scavenging stroke.

Provided is an internal combustion engine control device capable of reducing a measurement load and calculating a flow velocity around an ignition plug. The internal combustion engine control device includes an inter-gap voltage calculation unit 31 and a flow velocity calculation unit 32. The inter-gap voltage calculation unit 31 calculates a reference inter-gap voltage under a reference condition, based on a secondary current and in-cylinder pressure. The flow velocity calculation unit calculates the flow velocity of a gas around the ignition plug based on the reference inter-gap voltage.

An engine system includes a combustion chamber and an air supplier. The combustion chamber is formed in a cylinder. The air supplier is configured to supply air to a circumferential area of the combustion chamber. The circumferential area is near an inner circumferential surface of the cylinder. The air supplier is configured to supply air to the circumferential area before ignition to gather a rich air-fuel mixture that is present in the combustion chamber to a central area of the combustion chamber such that a stratified body consisting of a layer of the air-fuel mixture in the central area and a layer of the air in the circumferential area is formed.

An engine system includes a combustion chamber and an air supplier. The combustion chamber is formed in a cylinder. The air supplier is configured to supply air to a circumferential area of the combustion chamber. The circumferential area is near an inner circumferential surface of the cylinder. The air supplier is configured to supply air to the circumferential area before ignition to gather a rich air-fuel mixture that is present in the combustion chamber to a central area of the combustion chamber such that a stratified body consisting of a layer of the air-fuel mixture in the central area and a layer of the air in the circumferential area is formed.

Provided is a two-stroke internal combustion engine, including: a fuel injection valve configured to supply a fuel into a crank chamber; an intake passage configured to allow only air to be sucked thereinto under a negative pressure generated when a piston is actuated; and a scavenging passage that allows communication between the crank chamber and a combustion chamber. Further, air passing through the intake passage is introduced into the scavenging passage, and air stagnant in the scavenging passage at end of air suction contributes to scavenging.

A combustion system is provided for an internal combustion engine including a cylinder head and a piston. In one example, a combustion system may include a cylinder head with a second cylinder surface angled relative to a first cylinder surface, an intake port coupled to the first cylinder surface, an exhaust port coupled to the second cylinder surface, and a piston with a first piston surface parallel to the first cylinder surface and a second piston surface parallel to the second cylinder surface.

A compression ignition (diesel) engine uses two or more fuel charges during a combustion cycle, with the fuel charges having two or more reactivities (e.g., different cetane numbers), in order to control the timing and duration of combustion. By appropriately choosing the reactivities of the charges, their relative amounts, and their timing, combustion can be tailored to achieve optimal power output (and thus fuel efficiency), at controlled temperatures (and thus controlled NOx), and with controlled equivalence ratios (and thus controlled soot). At low load and no load (idling) conditions, the aforementioned results are attained by restricting airflow to the combustion chamber during the intake stroke (as by throttling the incoming air at or prior to the combustion chamber's intake port) so that the cylinder air pressure is below ambient pressure at the start of the compression stroke.