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    • 专利摘要:
    Ligger under intern notat (word-dok.)
    公开号:DK201670955A1
    申请号:DKP201670955
    申请日:2016-12-01
    公开日:2018-02-05
    发明作者:Johan Hult；Morten Kjul；Johan Sjoeholm
    申请人:Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland；
    IPC主号:
    专利说明:

    A FUEL VALVE FOR INJECTING A LIQUID FUEL INTO A COMBUSTION CHAMBER OF A LARGE COMPRESSION IGNITING TURBOCHARGED TWO-STROKE INTERNAL COMBUSTION ENGINE
    FIELD
    The present disclosure relates to a fuel valve for injecting fuel into a combustion chamber of a large two-stroke turbocharged compression-ignition internal combustion engine with a fuel supply system operating with liquid fuel, in particular difficult or unreliable to ignite liquid fuel and to a method for injecting a liquid fuel, in particular a liquid fuel that is difficult or unreliable to ignite in the combustion chamber of a large two stroke compression-ignition internal combustion engine.
    BACKGROUND ART
    Large low-speed turbocharged two-stroke compression-igniting engines of the crosshead type are typically used in propulsion systems of large ships or as prime mover in power plants. Very often, these engines are operated with heavy fuel oil.
    Recently, there has been a demand for large turbocharged two-stroke compression-igniting engines to be able to handle alternative types of fuel, such as gas, methanol, coal slurry, water-oil mixtures, petroleum coke and others.
    Several of these alternative fuels, such as water-oil mixtures, have the potential to reduce costs and emissions.
    However, there are problems associated with using water mixtures in a large low-speed uniflow turbocharged two-stroke internal combustion engine.
    One of those problems is the willingness and predictability of these fuels to compress-ignite upon injection into the combustion chamber and both willingness and predictability are essential to have under control in a compression-ignited engine. Therefore, existing large low-speed uniflow turbocharged two-stroke internal combustion engines use pilot injection of oil or other ignition liquid simultaneously with the injection of the difficult or unreliable to ignite fuel to ensure reliable and properly timed ignition of the fuel. The problem is present for several types of fuels that are challenging to ignite, such as e.g. fuel oil-water mixtures.
    Large low-speed uniflow turbocharged two-stroke internal combustion engines are typically used for the propulsion of large ocean going cargo ships and reliability is therefore of utmost importance. Operation of these engines with alternative fuels is still a relatively recent development and reliability of the operation with gas has not yet reached the level of conventional fuel. Therefore, existing large low-speed two-stroke diesel engines are all dual fuel engines with a fuel system for operation on an alternative fuel such as e.g. gaseous fuel and a fuel system for operation with fuel oil so that they can be operated at full power running on the fuel oil only.
    Due to the large diameter of the combustion chamber of these engines, they are typically provided with three fuel injection valves per cylinder, separated by an angle of approximately 120 ° around the central exhaust valve. Thus, with a dual fuel system there will be three fuel alternative fuel valves per cylinder and three conventional fuel oil valves per cylinder and thus, the top cover of the cylinder is a relatively crowded place.
    In the existing dual fuel engines the fuel oil valves have been used to provide the pilot oil injection during operation with gaseous fuel. These fuel oil valves are dimensioned so as to be able to deliver fuel oil in an amount required to operate the engine at full load on fuel oil only. However, the amount of oil injected into a pilot injection should be as small as possible to obtain the desired reduction in emissions. Dosage of such a small amount with a full size fuel injection system that can also deliver the large amount necessary for operation at full load poses significant technical problems, and is in practice very difficult to achieve and therefore the pilot oil dosage has been in existing engines with a larger quantity per fuel injection event than desirable, especially at medium and low load. The alternative of an additional small injection system that can handle the small pilot amount is a considerable complication and cost up. Further, additional small pilot oil injection valves render the top cover of the cylinder even more crowded.
    In general, it is not desirable to operate with a separate pilot injection of ignition liquid for several reasons. It has proved difficult to obtain a reliable injector operation below 3% of the MCR load. Secondly any external ignition, out in the cylinder, will require at least a minimum amount of fuel. The long term function of the pilot injection has further not been verified. It is expected that worn down fuel pumps might degrade the pilot injection function. Additionally, it is expected that the rapid pilot injection profile could cause increased wear on the fuel system.
    Some of these fuels also have a low flashpoint which gives rise to safety concerns. The construction of known fuel valves, always has leakage between the shaft of the valve needle and the drill into which the shaft is guided, due to the design of the needle. Therefore, a supply of pressurized sealing liquid 'sealing oil' is applied to the clearance between the shaft and the drill, both for sealing purposes but also for lubrication purposes. In order to keep leakage to a minimum the clearance is kept as small as possible with very narrow tolerances and such a small clearance requires lubrication between the shaft and the drill.
    Separation of sealing oil and fuel is difficult, in case the two fluids have been mixed thus causing error in the system. Detection of fuel in the lubrication oil system will result in shut down of the engine, and it is often difficult to trouble shoot the root cause.
    Another safety related issue is the requirement by the ship classification societies that low flashpoint fuels are not allowed to remain in the fuel valves and the tubing leading to the fuel valves when the engine is not operated on the low flashpoint fuel, e.g. when the engine is not operating or when it is a dual fuel engine that is operated on another type of fuel. Thus, provisions have to be made for purging the fuel valves and the tubing or piping leading to the fuel valves.
    Another challenge of these low flashpoint fuels is their relatively poor lubrication properties, which prevents the use of very small clearances between moving parts without applying a lubrication liquid.
    DISCLOSURE
    Against this background, it is an object of the present application to provide a fuel valve for a large turbocharged compression-ignited two-stroke internal combustion engine that overcomes or at least reduces the problems indicated above.
    This object is achieved according to one aspect achieved by providing a fuel valve for injecting liquid fuel into the combustion chamber of a large slow running two-stroke turbocharged compression-igniting internal combustion engine, the fuel valve comprising an elongated valve housing with a rear end and a front end, a nozzle comprising an elongated nozzle body extending from a base to a closed tip, a main bore extending from the base to the closed tip and a plurality of nozzle holes connected to the main bore, the nozzle being disposed at the front end of the elongated valve housing with the base connected to the front end, a fuel inlet port in the elongated fuel valve housing for connection to a source of pressurized liquid fuel, an axially displaceable valve needle slidably received in a longitudinal needle bore in the elongated valve housing with a clearance between the valve needle and the needle bore, the valve needle having a closed position and an open position, the valve needle rests on a valve seat in the closed position and the valve needle has lift from the valve seat in the open position and the valve needle being biased towards the closed position, the seat being disposed in the elongated valve housing between a fuel chamber in the valve housing and an outlet port at the front end of the elongated valve housing, the outlet port connecting directly to the main bore in the nozzle, the fuel chamber being connected to the fuel inlet port, the clearance opening at one end of the needle bore to the fuel chamber, a lubricating oil inlet port for connection to a source of pressurized lubricating oil, a lubricating oil supply conduit connecting the lubricating oil inlet port to the clearance at a first position along the length of the needle bore, an ignition liquid inlet port for connection to a source of pressurized ignition liquid, and an ignition liquid conduit extending from the ignition liquid inlet port to the chamber or to the clearance at a second position alo ng the length of the needle drill which is closer to the fuel chamber than the first position.
    The advantage of supplying an ignition liquid into the nozzle of the fuel injection vale that injects the difficult to ignite liquid fuel is that the engine can operate without an external pilot injection via a separate pilot valve. The ignition instead takes place inside the nozzle of the fuel valve which injects the difficult to ignite liquid fuel. The ignition liquid ignites inside the chamber in the nozzle where the initial flame is sheltered from the combustion chamber, giving it a better probability of igniting the liquid fuel that follows after or simultaneously during the injection event. This allows for a significantly reduced ignition-liquid consumption. Tests have indicated that levels below 1% of MCR load are possible.
    By providing an independent supply of ignition liquid, separate from e.g. the lubricating oil system, the dosage of ignition liquid can be controlled more accurately and reliably and the type of ignition liquid can be easily changed. Full control of the ignition liquid quantity, is achieved by varying upstream clearances and supply pressure, without compromising the action of the sealing oil system. The ignition liquid is no longer restricted to system oil. For example, more easily ignited liquids, such as diesel oil or DME (Dimethyl ether), can be used.
    In a first possible implementation of the first aspect, the ignition liquid conduit extends from the ignition inlet port to the fuel chamber at a position adjacent to the seat.
    In a second possible implementation of the first aspect, the ignition liquid conduit extends from the ignition inlet port to the seat.
    In a third possible implementation of the first aspect the ignition liquid conduit to the seat is closed by the valve needle when the valve needle rests on the seat.
    In a fourth possible implementation of the first aspect the main bore opens to the base.
    In a fifth possible implementation of the first aspect, the source of ignition liquid has a pressure that is higher than the pressure of the source of liquid fuel.
    In a sixth possible implementation of the first aspect, the fuel valve further comprises an actuation liquid port in the elongated fuel valve housing for connection to a source of pressurized actuation fluid, a pump piston received in a first bore in the valve housing with a pump chamber in the first bore on one side of the pump piston, an actuation piston received in a second bore in the valve housing with an actuation chamber in the second bore on one side of the actuation piston, the pump piston being connected to the actuation piston to move in unison therewith, the actuation chamber being fluidly connected to the actuation liquid port, and the pump chamber having an outlet connected to the fuel chamber and an inlet connected to the fuel inlet port via a nonreturn valve in the elongated fuel valve housing that prevents flow from the pump chamber to the fuel inlet port.
    In a seventh possible implementation of the first aspect, the fuel chamber surrounds the valve needle and opening to the valve seat with the valve seat being arranged between the fuel chamber and the outlet port
    In an eighth possible implementation of the first aspect the valve needle is configured to move from the closed position to the open position against the bias when the pressure in the fuel chamber exceeds a predetermined threshold.
    In a ninth possible implementation of the first aspect the fuel valve further comprises a cooling liquid inlet port and a cooling liquid outlet port and a cooling liquid flow path for cooling the fuel injection valve, in particular the portion of the fuel valve closest to the front than.
    In a tenth possible implementation of the first aspect, the elongated valve housing comprises a front portion connected to a rear portion, the axially displaceable valve needle disposed in the front portion, the first bore, the second bore and the matching longitudinal bore being formed in the rear portion.
    In an eleventh possible implementation of the first aspect, the fuel valve further comprises a conduit connecting the sealing liquid inlet port to the first bore for sealing the pump piston in the first bore.
    According to a second aspect, a large slow running two-stroke turbocharged compression-igniting internal combustion engine comprising a fuel valve is provided according to the first aspect of any possible implementations thereof.
    In a first possible implementation of the second aspect, the engine further comprises a source of pressurized fuel with a controlled pressure Pf, a source of pressurized lubricating oil with a controlled pressure Ps and a source of pressurized ignition liquid with a controlled pressure Pif.
    In a first possible implementation of the second aspect Ps is higher than Pf and Pif is higher than Pf.
    In a first possible implementation of the second aspect the engine is configured to ignite the fuel upon entering the fuel into the main bore inside the nozzle.
    According to a third aspect, a method of operating a large two-stroke low-speed turbocharged compression-ignited internal combustion engine is provided, the method comprising providing pressurized liquid fuel at a first high pressure to a fuel valve of the engine, the fuel valve having an elongated valve housing with a rear end and a front end, the fuel valve having a hollow nozzle with a plurality of nozzle holes connecting the interior of the nozzle to a combustion chamber in a cylinder of the engine, the nozzle comprising a base and an elongated nozzle body, the nozzle being connected with its base to the front end of the elongated valve housing, the nozzle having a closed tip with the nozzle holes arranged close to the tip, supplying ignition liquid at a second high pressure to the fuel valve, the second high pressure being higher than the first high pressure, controlling the injection of the liquid fuel with a displaceable valve needle that cooperates with a seat above the ho llow nozzle, a fuel chamber being arranged above the seat, pressurizing the fuel chamber with the liquid fuel, delivering a small continuous flow of ignition liquid to the fuel chamber and allowing the ignition liquid to accumulate above the seat during periods where the axially displaceable valve needle rests on the seat and starts a liquid fuel injection event by lifting the axially displaceable valve needle from the seat, thereby causing the accumulated ignition liquid to enter the hollow injection nozzle just ahead of the liquid fuel, or delivering a precisely dosed amount of ignition liquid to the seat when the axially displaceable valve needle has lift, and starting a liquid fuel injection event by lifting the axially displaceable valve needle from the seat, thereby causing the accumulated ignition liquid to enter the hollow injection nozzle simultaneously with the liquid fuel.
    In a first possible implementation of the third aspect, the liquid fuel ignites inside the nozzle with the help of the ignition liquid.
    In a first possible implementation of the third aspect the nozzle is kept above 300 ° C throughout the engine cycle.
    Further objects, features, advantages and properties of the fuel valve and engine according to the present disclosure will become apparent from the detailed description.
    LETTER DESCRIPTION OF THE DRAWINGS
    In the following detailed portion of the present description, the invention will be explained in more detail with reference to the exemplary embodiments shown in the drawings, in which:
    FIG. 1 is a front view of a large two-stroke diesel engine according to an example embodiment,
    FIG. 2 is a side view of the large two-stroke engine of FIG. 1
    FIG. 3 is a diagrammatic representation of the large two stroke engine according to FIG. 1, and
    FIG. 4 is a diagrammatic representation of an exemplary embodiment of a low fuel system fuel system of FIG. 1
    FIG. 5 is a sectional view in diagrammatic representation of an example embodiment of the engine fuel system of FIG. 1 of the upper part of a cylinder,
    FIG. 6 is an elevated view of a fuel valve for using an engine according to Figs. 1 to 3 to an example embodiment,
    FIG. 7 is a sectional view of the fuel injection valve shown in FIG. 6
    FIG. 7A shows a first embodiment of an enlarged detail of FIG. 7
    FIG. 7B shows a second embodiment of an enlarged detail of FIG. 7
    FIG. 7C shows a third embodiment of an enlarged detail of
    FIG. 7
    FIG. 7D shows a fourth embodiment of an enlarged detail of FIG. 7
    FIG. 8 is a different sectional view of a low flashpoint fuel injection valve shown in FIG. 6
    FIG. 9 is another different sectional view of a low flashpoint fuel injection valve shown in FIG. 6
    FIG. 9A shows an enlarged detail of FIG. 9th
    FIG. 10 is another different sectional view of a low flashpoint fuel injection valve shown in FIG. 6, and FIG. 11 is another different sectional view of a low flashpoint fuel injection valve shown in FIG. 6th
    DETAILED DESCRIPTION
    In the following detailed description, the compression-igniting internal combustion engine will be described with reference to a large two-stroke low-speed turbocharged internal combustion (Diesel) engine in the example embodiments. Figs. 1, 2 and 3 show a large low-speed turbocharged two-stroke diesel engine with a crankshaft 42 and crossheads 43. FIG. 3 shows a diagrammatic representation of a large low-speed turbocharged two-stroke diesel engine with its intake and exhaust systems. In this example embodiment the engine has four cylinders 1 in line. Large low-speed turbocharged two-stroke diesel engines typically have between four and fourteen cylinders in line, carried by an engine frame 13. The engine may e.g. used as the main engine in an ocean going vessel or as a stationary engine for operating a generator in a power station. The total output of the engine may, for example, range from 1,000 to 110,000 kW.
    In this example, the engine is a two-stroke uniflow type diesel (compression-igniting) engine with scavenge ports 19 at the lower region of the cylinders 1 and a central exhaust valve 4 at the top of the cylinders 1. The scavenge air is passed from the scavenge air receiver 2 to the scavenge ports 19 of the individual cylinders 1. A piston 41 in the cylinder 1 compresses the scavenge air, fuel is injected from fuel injection valves (described in detail further below), into the cylinder cover (described in detail further below), combustion follows and exhaust gas is generated. When an exhaust valve 4 is opened, the exhaust gas flows through an exhaust duct associated with the cylinder 1 into the exhaust gas receiver 3 and onwards through a first exhaust conduit 18 to a turbine 6 of the turbocharger 5, from which the exhaust gas flows away through a second exhaust conduit via an economizer 28 to an outlet 29 and into the atmosphere. Through a shaft, the turbine 6 drives a compressor 9 supplied with fresh air via an air inlet 10. The compressor 9 delivers pressurized scavenge air to a scavenge air conduit 11 leading to the scavenge air receiver 2.
    The scavenge air in conduit 11 passes an intercooler 12 for cooling the scavenge air. In an example embodiment the scavenge air leaves the compressor at approximately 200 ° C and is cooled to a temperature between 36 and 80 ° C by the intercooler.
    The cooled scavenge air passes through an auxiliary blower 16 driven by an electric motor 17 that pressurizes the scavenge air flow when the compressor 9 of the turbocharger 5 does not deliver sufficient pressure for the scavenge air receiver 2, i.e. in low or partial load conditions of the engine. At higher engine, the turbocharger compressor 9 delivers sufficiently compressed scavenge air and then the auxiliary blower 16 is bypassed via a non-return valve 15.
    FIG. 4 is a diagrammatic representation of a liquid fuel valve 50 with its connections to the source of liquid fuel 60 (such as eg oil-water fuel or a low flashpoint fuel such as eg methanol), to a source of cooling liquid (oil) 63 , to the source of lubricating liquid 57, to a source of ignition fluid 65, to a source of actuation liquid (oil) 97 via a control valve 96, to a purge control valve 98, and to an actuation liquid control valve 98.
    A conduit 62 leads from the source of pressurized liquid fuel 62 to the inlet port in the housing of the liquid fuel valve 50. Conduit 62 can be a double walled conduit, e.g. formed by concentric tubes or by a tube inside a solid block material such as the cylinder cover 48, A window valve 61 can be provided in the conduit 62 for being able to disconnect the fuel valve 50 from the source of liquid fuel 60 for being able to to purge the fuel valve 50 from flashpoint fuel. The window valve 61 is preferably electronically operated and controlled by the electronic control unit. The electronic control valve 96 controls the injection events and the purge control valve 98 controls purging by preventing a non-return valve from closing.
    FIG. 5 shows the top of one of the plurality of cylinders 1 according to an example embodiment. The top cover 48 of the cylinders 1 is provided with a number (typically 2 or 3) of fuel valves 50 for injecting a liquid fuel from a nozzle of the fuel valves 50, into the combustion chamber above the piston 41 in the cylinder 1. In this example, the engine has three liquid fuel valves 50 per cylinder, but it should be understood that a single or two fuel valves 50 may be sufficient, depending on the size of the combustion chamber. The exhaust valve 4 is placed centrally in the top cover with the liquid fuel valves 50 closer to the cylinder wall.
    In one embodiment (not shown), two or three additional fuel oil valves can be provided in the top cover 48 for operation of the engine on fuel oil. The fuel oil valves are connected to a source of high pressure fuel oil in a well-known manner.
    The forward portion of the fuel valve 50 which is closest to the nozzle and closest to the combustion chamber is cooled in an embodiment using a cooling liquid, such as cooling oil, for which system oil (lubrication oil) can be used. Hereto, the body of the fuel valve 50 is provided with a cooling liquid inlet port and a cooling liquid outlet port and a flow path (not shown) between the in port and the outlet port through the forward portion of the body of the fuel valve 50. The cooling liquid inlet port is connected via a conduit to a source of pressurized cooling liquid 63, such as system oil, and the cooling liquid outlet port is connected via a conduit to a reservoir of cooling liquid.
    The body of the fuel valve 50 is also provided with an actuation liquid port for controlling the opening and closing of the fuel valve 50. The control port is connected via a conduit to the source of pressurized actuation liquid 97. The electronically controlled control valve 96 , preferably a proportional valve, is placed in the conduit between the source of pressurized actuation liquid 97 and the actuation liquid port for controlling the opening and closing of the fuel valve 50, ie for controlling injection event.
    The body of the fuel valve 50 is also provided with an ignition liquid inlet port for receiving ignition liquid from a pressurized source of ignition liquid 65 at a pressure Pif.
    The engine is provided with an electronic control unit (not shown) that controls the operation of the engine. Signal lines connect the electronic control unit to the electronic control valves 96 and 98 and to the window valves 61.
    The electronic control unit is configured to time the injection events of the liquid fuel valve 50 correctly and to control the dosage (volume injected per injection event) of the liquid fuel with the fuel valves 50. The electronic control unit is configured in an embodiment to control the shape of the injection curve (rate shaping), since the fuel valve is capable of adapting to such curves.
    In a configuration with low flashpoint fuel, the electronic control unit opens and closes window valve 61 to ensure that the supply conduit 62 is filled with pressurized low flashpoint liquid fuel before the start of a fuel injection event. The window valve 61 is closed by the electronic control unit when the fuel valve 50 needs to be purged from low flashpoint fuel.
    FIG. 6 is a perspective view of the fuel valve 50 with its elongated valve housing 52, a nozzle 54 attached to the front end of the elongated valve housing 52 and a lubricating liquid inlet port 70 and a control port 36 for controlling purging. The nozzle 54 is provided with a plurality of nozzle holes 56 that are radially and axially distributed over the nozzle 54.
    Figs. 7,8,9,10 and 11 show sectional views of a fuel valve 50 for injecting liquid fuel into the combustion chamber 41 of the compression-igniting internal combustion engine. The fuel valve 50 has an elongated valve housing 52 with a rearmost end and a nozzle 54 attached to its front end. The nozzle 54 is a separate body attached with its base 46 to the front end of valve housing 52. The rearmost end of valve housing 52 is provided with a plurality of ports, including a (purge) control port 36, an actuation liquid port 78, an ignition liquid port 67 and a gas leak detection port (not shown). The rearmost end is enlarged to form a head which protrudes from the cylinder cover 48 when the fuel valve 50 is mounted in the cylinder cover 48. In the present embodiment, the fuel valves 50 are placed around the central exhaust valve 4, i.e. relatively close to the wall of the cylinder liner. The elongated valve housing 52 and the other components of the fuel injection valve 50 as well as the nozzle are embodiments of steel, such as e.g. tool steel and stainless steel.
    The hollow nozzle 54 is provided with nozzle holes 56 which are connected to the main bore 55 in the nozzle 54 and the nozzle holes 56 are distributed radially and preferably also over the nozzle 54. The nozzle holes 56 are axially close to the closed tip. 59 and the radial distribution of the nozzle holes 56 is in the present embodiment over a relatively narrow range of approximately 50 °. The radial orientation of the nozzle holes 56 is such that the nozzles holes 56 are directed away from the wall of the cylinder liner. Further, the nozzle holes 56 are directed such that they are roughly in the same direction as the direction of the swirl of the scavenge air in the combustion chamber caused by the slanted configuration of the scavenge ports (this swirl is a well-known feature of large two-stroke turbocharged internal combustion engines of the uniflow type).
    The tip 59 of the nozzle 54 is closed, i.e. there is no downwardly directed nozzle hole 46. The nozzle 54 is connected with its base 46 to the front end of the valve housing 52 with the main bore of the nozzle 54 opening towards an outlet opening 68 in the front end of the valve housing 52. A valve seat 69 is disposed at the transition between an axial bore forming the outlet opening 68 and a fuel chamber 58.
    An axially displaceable valve needle 61 is slidably received with a narrow clearance in a longitudinal bore in the elongated valve housing 52, and lubrication between the axially displaceable valve needle 61 and the longitudinal bore is critical. Hereto, pressurized lubricating liquid is delivered to the clearance between the longitudinal bore 64 in the valve needle via a conduit (channel) 47. The channel 47 connects the clearance between the valve needle 61 and the axial bore to the lubricating oil inlet port 70, which in turn can be connected to the source of pressurized lubricating oil 57 which is pressurized and a pressure Ps. The lubricating oil prevents leakage of fuel into the clearance between valve needle 61 and the axial bore when operating on low flashpoint fuel. Further, the lubricating oil provides for lubrication between the valve needle 61 and the axial bore 64. In one embodiment, the pressure of the source of lubricating oil 57 is at least above the supply pressure of the source of liquid fuel but can be well below the maximum pressure in the pump chamber 82 during an injection event as long as the aggregate flow in the clearance between the pump piston 80 and the 1st bore 81 is in the direction towards the pump chamber 82.
    The valve needle 61 has a closed position and an open position. The valve needle 61 is provided with a conical section which is shaped to match the valve seat 69. In the closed position the conical section of the valve needle rests on the valve seat 69. The conical section has lift from the valve seat 69 in the Open position and valve needle 61 is resiliently biased toward the closed position by a pre-tensioned helical spring 38. The pretensioned helical spring 38 acts on the valve needle 61 and biases the valve needle 61 toward its closed position where the conical section rests on the seat 69.
    The helical spring 38 is a helical wire spring that is received in a spring chamber 88 in the elongated fuel valve housing 52. Cooling oil flows through the spring chamber 88. One end of the helical spring 38 engages an end of the spring chamber 88 and the other end of the helical spring 38 engages a widened section or flange on the valve needle 61, thereby resiliently urging the valve needle toward the valve seat 69.
    The elongated valve housing 52 is provided with a fuel inlet port 53 for connection to a source of pressurized liquid fuel 60, via the low fuel supply conduit 62. The fuel inlet port 53 connects to a pump chamber 82 in the valve housing 52 via a conduit 51 and a non-return valve 7. The non-return valve 74 (suction valve) is provided inside the valve housing 52. The non-return valve 74 ensures that liquid fuel can flow through the conduit 51 to the pump chamber 82, but not in the opposite direction. A pump piston 80 is slidably and sealingly disposed in a first bore 81 in the elongated fuel valve housing 52 with a pump chamber 82 in the first bore 81 on one side of the pump piston 80. An actuation piston 83 is slidably and sealingly disposed in a second bore 84 in the valve housing 52 with an actuation chamber 85 in the second bore 84 on one side of the actuation piston 83. The pump piston 80 is connected to the actuation piston 83 to move in unison therewith, ie the pump piston 80 and the actuation piston 83 can slide in unison their respective bores 81.84. In the present embodiment the pump piston 80 and the actuation piston 83 performed by a single body, however, it is noted that the pump piston 80 and the actuation piston 83 can be separate interconnected bodies.
    The actuation chamber 85 is fluidly connected to an actuation liquid port 78. The electronic control valve 96 controls the flow pressurized actuation liquid to and from the actuation liquid port 78 and thereby to and from the actuation chamber 85.
    At the start of injection event, the electronic control unit commands the electronic control valve 96 to allow actuation liquid into the actuation chamber 85. The pressurized actuation liquid in the actuation chamber 85 acts on the actuation piston 83, thereby creating a force that urges the pump piston 81 into the pump chamber 82. Thereby the pressure of the liquid fuel in the pump chamber 82 increases. In embodiment the diameter of the actuating piston 83 is greater than the diameter of the pump piston 8 0 and thus the pressure in the pump chamber 82 will be correspondingly higher than the pressure in the actuating chamber 85 and the combination of the actuating piston 83 and pump piston 80 acts as a pressure booster.
    One or more channels (conduits) 57 fluidly connect the pump chamber 82 to the fuel chamber 58 and thereby to the valve seat 69 which is located at the bottom of the fuel chamber. The valve seat 69 faces the fuel chamber 58 which surrounds the valve needle 61. The valve needle 61 is configured to move away from the nozzle 54 to obtain lift, and toward the nozzle 54 to reduce lift. In its open position, the valve needle 61 has lift from the seat 69 thereby allowing flow of liquid fuel from the pump chamber 82 to the fuel chamber 58, pasting the valve seat 69 and via an outlet port 68 to the main bore 55 in the nozzle 54. The low flashpoint liquid leaves the main bore 55 via the nozzle holes 56.
    The valve needle 61 gets lifted when the pressure of the liquid fuel in the pump chamber 82 exceeds the force of the helical spring 38. Thus, the valve needle 61 is configured to open against the bias of the spring 38 when the pressure of the fuel in the pump chamber 82 (and in the fuel chamber 55) exceeds a predetermined threshold. The pressure in the fuel is caused by the pump piston 80 acting on the low flashpoint liquid fuel in the pump chamber 82.
    The valve needle 61 is configured to be biased toward the nozzle 54 with the conical section moving toward the valve seat 69. This happens when the pressure in the liquid fuel decreases when the pump piston 80 no longer acts on the fuel in the pump chamber 82 and the closing force of the helical spring 38 on the valve needle 61 becomes larger than the opening force of the low flashpoint liquid fuel on the valve needle 61.
    When the electronic control unit ends an injection event, it commands the electronic control valve 96 to connect the actuation chamber 85 to the tank. The pump chamber 82 is connected to the pressurized source of liquid fuel 60 and the supply pressure of the low flashpoint liquid fuel flowing through the non-return valve 74 will urge actuation piston 83 into the actuation chamber 85 until it has reached the position which is shown in FIG. 7 with the pump chamber 82 completely filled with liquid fuel so that the fuel valve 50 is ready for the next injection event. FIG. 8 shows the position of the pump piston 82 and the actuation position 83 near the end of an injection event with a major portion of the pump chamber 80 depleted from liquid fuel.
    An injection event of the liquid fuel is controlled by the electronic control unit ECU through the length of the activation timing and the length of the stroke of the pump piston 82 (rate shaping). The amount of low fuel injected in one injection event is determined by the length of the stroke of the pump piston 80. Thus, upon a signal from the electronic control unit, the actuation liquid pressure is raised in the actuation chamber 85.
    At the end of the injection event, the electronic control valve 96 removes the pressure from the actuation chamber 85 and the force of the pressurized liquid fuel in the pump chamber 82 causes the actuation piston 83 to be pushed back in the second bore 85 until it hits the end of the second bore 85 and the pump chamber 82 is completely filled with liquid fuel and the fuel valve 50 is ready for the next injection event.
    In an embodiment (not shown) the fuel valve 50 comprises pressure booster form of a plunger with two different diameters, with the large diameter part of the plunger facing a chamber with a port connected to the control valve 96 and the larger diameter part of the plunger facing a chamber with a port connected to the conduits (channel) 51 and 47 so as to boost the lubricating oil pressure during a fuel injection event thus ensuring that the lubricating pressure is high exactly at the time when it is most needed to provide high lubricating pressure.
    The fuel valve 50 is provided with a lubrication oil inlet port 70 for connection to a source of pressurized lubrication oil and provided with a conduit 30 extending from the lubrication oil inlet port 70 to the first bore 81 for sealing and lubricating the pump piston 80 in the first bore 81. In one embodiment, the pressure of the source of lubrication oil 57 is at least almost as high as the maximum pressure in the pump chamber 82 during an injection event.
    In an embodiment, the fuel valve 50 is provided with means to selectively allow flow from the pump chamber 82 towards the fuel inlet port 53 for purging the fuel valve 50. The means to selectively allow flow from the pump chamber 82 towards the fuel inlet port 53 comprise means to selectively deactivate the non-return function of the non-return valve 74 (suction valve).
    The valve needle 69 is configured to move from the closed position to the open position against the bias of the helical spring 38 when the pressure in the fuel chamber 58 exceeds a predetermined threshold.
    The elongated valve housing 52 is provided in an embodiment with a cooling liquid inlet port 45 and a cooling liquid outlet port 32 and a cooling liquid flow path 44 for cooling the fuel injection valve 50, in particular the portion of the fuel valve 50 closest to the front end, eg closest to the nozzle and heat from the combustion chamber. The cooling liquid is an embodiment of system lubrication oil from the engine. In an embodiment, the cooling liquid flow path includes spring chamber 88 in which helical spring 38 is received.
    In an embodiment, the elongated valve housing 52 comprises a front portion 33 which is connected to a rear portion 35. The axially displaceable valve needle 61 is disposed in the front portion 33, the first bore 81, the second bore 84 and the matching longitudinal bore. being formed in the rear portion 35.
    The fuel valve 50 is in an embodiment provided a conduit 47 extending from the sealing and lubrication liquid inlet port 70 to the longitudinal needle bore 64 at a position PI along the length of the longitudinal needle bore 64 for sealing the valve needle 61 in the longitudinal needle bore 64. The sealing oil flows from position PI through the clearance both upward to the chamber surrounding the helical spring and downward toward the fuel chamber 58. The portion of the ignition liquid that flows to the actuation chamber 74 mixes with the cooling oil. This has no substantial effect on the cooling oil.
    In the present first embodiment, the portion of the ignition liquid that flows to the fuel chamber 58 meets the pressure of ignition liquid supplied to the clearance by an ignition liquid conduit 66 which extends from the ignition liquid inlet port 67 through the valve housing 52 to the clearance at a position P2 that is closer to the fuel chamber 58 than position PI. The ignition liquid inlet port 67 is connected to the source of pressurized ignition liquid 65. Since the pressure of the sealing oil is higher than that of the ignition liquid the sealing oil will prevent ignition liquid from leaking back into the sealing oil system.
    The ignition fluid delivered to the clearance via the ignition liquid conduit 66 migrates along the axial extension of the clearance to the fuel chamber 58 and and accumulates at the bottom of the fuel chamber 58 i.e. just above the seat 69 while the axially movable valve needle 61 rests on the seat 69, as shown in FIG. 7a.
    The dimensions of the clearance are precisely controlled and selected so that the appropriate amount of ignition liquid is collected at the bottom of the fuel chamber 58 at the time during an engine cycle where the axially movable valve member 61 rests on the seat 69. An appropriate amount of ignition liquid is the amount sufficient to create a reliable and stable ignition, for example be in the range of 0.1 mg to 200 mg, depending on eg on the engine size and load. The dimensions of the clearance are chosen in relation to the properties of the ignition liquid, such as e.g. viscosity, that a constant flow of ignition liquid of an appropriate magnitude is achieved when the source of ignition liquid has a pressure that is a margin above the pressure of the source of the liquid fuel.
    Upon a signal from the electronic control unit, the liquid fuel pressure is raised to the fuel chamber 58 and the valve needle 61 is lifted from the seat 69 in a movement from its closed position to its open position. The ignition liquid accumulated at the bottom of the fuel chamber 58 (Fig. 7a) enters the main bore 55 in the nozzle 54 first, followed by the liquid fuel, i.e. the liquid fuel pushes the ignition liquid ahead and into the main bore 55. Thus, the ignition liquid that was accumulated in the combustion chamber 58 will enter the main bore 55 in the nozzle 54 just ahead of the liquid fuel. At the moment just before the opening of the fuel valve 50, the main bore 55 is filled with a mixture of compressed hot air and residual unburned fuel, due to the compression of the scavenging air in the combustion chamber (the nozzle holes 56 allow flow of air from the combustion chamber into the main bore 55). Thus, shortly after the opening of the fuel valve 50 there is hot compressed air, ignition liquid and liquid fuel present inside the main bore 55. This leads to ignition of the liquid fuel already inside the hollow nozzle 54.
    At the end of the injection event, the electronic control unit removes the pressure from the actuation chamber 85 and the force of the helical spring 38 causes valve needle 61 to return to seat 69.
    According to a second example embodiment which is essentially identical to the first example embodiment described above, the delivery of the ignition liquid is not to the clearance but instead to the seat 69. This embodiment is illustrated with reference to FIG. 7b. The ignition liquid conduit 66 opens to the seat 69. The opening angle of the conical tip of the valve needle 61 is slightly sharper than the opening angle of the conical seat 69 and thus there is a narrow gap between the tip of the valve needle and the valve seat 69. This narrow gap allows ignition liquid 49 to accumulate in the fuel chamber 58 at and just above the valve seat 69 whilst the valve needle 61 rests on its seat 69.
    According to a third example embodiment which is essentially identical to the embodiments described above, the delivery of the ignition liquid is to the fuel chamber 58. This embodiment is illustrated with reference to FIG. 7c. The ignition liquid conduit 66 opens to the fuel chamber 58, preferably just above or adjacent seat 69. Ignition liquid 49 accumulates in the fuel chamber 58 above the valve seat 69 whilst the valve needle 61 rests on its seat 69.
    According to a fourth example embodiment which is essentially identical to the embodiments described above, the delivery of the ignition is liquid to the seat 69. This embodiment is illustrated with reference to FIG. 7d. The ignition liquid conduit 66 opens to the seat 69. The opening angle of the conical tip of the valve needle 61 is substantially identical to the opening angle of the conical seat 69 and thus valve needle 61 closes off the opening of the ignition liquid conduit 66 to the valve seat when the valve needle 61 rests on the valve seat 69. Ignition liquid is delivered to the valve seat 69 through the ignition liquid conduit 66 opening to the valve seat 69 when the valve needle has lift. In this embodiment, the delivery of the appropriate amount of ignition liquid has to take place in a short period of time and therefore the supply pressure of the ignition liquid and or the cross-sectional area of the ignition liquid supply conduit 66 are increased relative to the embodiments described above.
    The injection of the liquid fuel is controlled with the displaceable valve needle 61 which cooperates with the seat 69 above the hollow nozzle 54. The fuel chamber 58 is pressurized with liquid fuel. A small continuous flow of ignition liquid is in accordance with the first, second and third embodiments delivered to the fuel chamber 58 and the ignition liquid 49 accumulates above the seat 69 during periods when the valve needle 61 rests on the seat 69 (embodiments According to Figs. 7a, 7b and 7c, a fuel injection event is started by lifting the axially movable valve needle 61 from the seat 69, thereby causing the accumulated ignition liquid 49 to enter the main bore 55 in the hollow injection nozzle 54 just ahead of the liquid fuel.The liquid fuel then ignites inside the nozzle 54 with the help of the ignition liquid.
    For the embodiment of FIG. 7d, the ignition liquid is delivered to the valve seat 69 when the valve needle 61 has lift and thus liquid fuel and ignition liquid is delivered to the main bore in the injection nozzle 45 simultaneously.
    The engine is configured to compress-ignite the injected liquid fuel with the help of the ignition liquid and without the use of other ignition equipment.
    The engine is configured to ignite the liquid fuel upon entering the main bore inside the nozzle 54.
    In an embodiment the nozzle 54 is maintained above 300 ° C throughout the engine cycle. In an embodiment the temperature inside the hollow nozzle 54 is approximately 600 degrees C at the end of the compression stroke.
    In an embodiment, the fuel valve 50 is provided with a dedicated control valve in a fluid connection between the pump chamber 82 and the fuel inlet port 53 for selectively allowing flow from the pump chamber 82 to the fuel inlet port 53 for purging of the fuel valve 50. This control valve is preferably opened and closed in response to a control signal. In this embodiment, it is not necessary to provide means to selectively deactivate the non-return function of the non-return valve 74.
    In an embodiment the source of lubrication oil has a controlled pressure Ps and a source of liquid fuel has a controlled pressure Pf, with Ps being higher than Pf. In this embodiment, the controlled pressure Ps can be lower than the maximum pressure in the pump chamber 82 during a pump stroke. In this case Ps, the size of the clearance and the maximum pressure in the pump chamber 82 during a pump stoke are interdependently selected such that if low flashpoint liquid fuel enters the clearance and replaces the lubrication liquid along a portion but not all of the length of the pump piston 80 and the sealing liquid replaces substantially all low flashpoint fuel in the clearance before another pump stroke takes place, any remaining of low flashpoint fuel so that there will not be ingress of low flashpoint fuel the lubrication oil system itself.
    The term "comprising" as used in the claims does not exclude other elements or steps. The term "a" or "an" as used in the claims does not exclude a plurality. The electronic control unit may fulfill the functions of several means recited in the claims.
    The reference signs used in the claims shall not be construed as limiting the scope.
    Although the present invention has been described in detail for purposes of illustration, it is understood that such detail is solely for that purpose, and variations may be made therein by those skilled in the art without departing from the scope of the invention.
    权利要求:
    Claims (4)
    [1] 1. A fuel valve (50) for injecting liquid fuel into the combustion chamber of a large slow running two-stroke turbocharged compression-igniting internal combustion engine, said fuel valve (50) comprising:
    an elongated valve housing front end, (52) with a rear end and a a nozzle (54) comprising an elongated nozzle body extending from a base (46) to a closed tip (59), a main bore (55) extending from said base (46) to said closed tip (59) and a plurality of nozzle holes (56) connected to said main bore (55), said nozzle (54) being disposed at said front end of said elongated valve housing (52) with said base (46) connected to said front end, a fuel inlet port (53) in said elongated fuel valve housing (52) for connection to a source (60) of pressurized liquid fuel, an axially displaceable valve needle (61) slidably received in a longitudinal needle bore (64) in said elongated valve housing (52) with a clearance between said valve needle (61) and said needle bore (64), said valve needle (61) having a closed position and an open position, said valve needle (61) rests on a valve seat (69) in said closed position and said valve needle (61) has lift from said valve seat (69) in said open position and said valve needle (61) being biased towards said closed position,
    02635-1I-DK-P
    DK 2016 70955 A1 said seat (69) being disposed in said elongated valve housing (52) between a fuel chamber (58) in said valve housing (52) and an outlet port (68) in said front end of said elongated valve housing (52),
    said outlet port (68) connecting directly to said main bore (55) in said nozzle (54), said fuel chamber (58) being connected to said fuel inlet port (53) , said clearance opening at one end of said needle bore (64) to said fuel chamber (58),
    a lubricating oil inlet port (70) for connection to a source of pressurized lubricating oil (57), a lubricating oil supply conduit (47) connecting said lubricating oil inlet port (70) to said clearance at a first position (Pl) along the length of the needle bore (64) , an ignition liquid inlet port (67) for connection to a source of pressurized ignition liquid (65), and an ignition liquid conduit (66) extending from said ignition liquid inlet port (67) to said chamber (58) or to said clearance at a second position (P2) along the length of said needle bore (64) that is closer to said fuel chamber (58) than said first position (Pl).
    [2] 2/7 M
    2S 6J
    DK 2016 70955 A1
    DK 2016 70955 A1
    2. A fuel valve according to claim 1, wherein said ignition liquid conduit (66) extends from said ignition
    02635-1I-DK-P
    DK 2016 70955 A1 inlet port (67) to the fuel adjacent the seat (69).
    chamber (58) at a position
    [3] 3. A fuel valve according ignition liquid conduit (66) inlet port (67) to said seat to claim 1, extends from (69) .
    wherein said said ignition
    4. A fuel valve according to claim 3, wherein an opening of said ignition liquid conduit (66) to said seat (69) is closed by the valve needle (61) when the valve needle (61) rests on said seat (69) .
    5. A fuel valve according to any one of claims 1 to 4, wherein said main bore (55) opens to said base (46).
    6. A fuel valve according to any one of claims 1 to 5, wherein said source of ignition liquid (65) has a pressure that is higher than the pressure of said source of liquid fuel (60) .
    7. A fuel valve according to any one of the preceding claims, further comprising an actuation liquid port (78) in said elongated fuel valve housing (52) for connection to a source (60) of pressurized actuation fluid, a pump piston (80) received in a first bore (81) in said valve housing (52) with a pump chamber (82) in said first bore (81) on one side of said pump piston (80), an actuation piston (83) received in a second bore (84) in said valve housing (52) with an actuation chamber (85) in said second bore (84) on one side of said actuation piston (83),
    02635-1I-DK-P
    DK 2016 70955 A1 said pump piston (80) being connected to said actuation piston (83) to move in unison therewith, said actuation chamber (85) being fluidically connected to said actuation liquid port (78), and said pump chamber (82) having an outlet connected to said fuel chamber (58) and an inlet connected to said fuel inlet port (53) via a non-return valve (74) in said elongated fuel valve housing (52) that prevents flow from said pump chamber (82) to said fuel inlet port (53).
    8. A fuel valve according to any one of the preceding claims, wherein said fuel chamber (58) surrounds said valve needle (61) and opening to said valve seat (69) with said valve seat (69) being arranged between said fuel chamber (58) and said outlet port (68)
    9. A fuel valve (50) according to any one ; of the preceding claims, wherein said valve needle (69) is configured to move from said closed position to said open position against said bias when the pressure in said fuel
    chamber (58) exceeds a predetermined threshold.
    10. A fuel valve (50) according to any one of the preceding claims, further comprising a cooling liquid inlet port and a cooling liquid outlet port and a cooling liquid flow path (44) for cooling the fuel injection valve (50), in particular the portion of the fuel valve (50) closest to said front end.
    11. A fuel valve (50) according to any one of the preceding claims, wherein said elongated valve housing (52) comprises a front portion (33) that is connected to
    02635-1I-DK-P
    DK 2016 70955 A1
    a rear portion (35) , said axially displaceable valve needle i (61) being disposed in said front portion (33) , said first bore (81), said second bore (84) and said matching longitudinal bore being formed in said rear portion (35) .
    12. A fuel valve (50) according to any one of claims 7 to 11, further comprising a conduit (30) connecting said sealing liquid inlet port (70) to said first bore (81) for sealing said pump piston (80) in said first bore.
    13. A large slow running compression-igniting internal comprising a fuel valve (50) preceding claims.
    two-stroke combustion according to turbocharged engine (1) any of the
    14. An engine according to claim 13, further comprising a source of pressurized fuel (60) with a controlled pressure Pf, a source of pressurized lubricating oil (57) with a controlled pressure Ps and a source of pressurized ignition liquid (65) with a controlled pressure Pif.
    15. An engine according to claim 14, wherein Ps is higher than Pf and wherein Pif is higher than Pf.
    16. An engine according to any one of claims 13 to 15 configured to ignite said fuel upon entry of the fuel in the main bore (55) inside the nozzle (54).
    17. A method of operating a large two-stroke low-speed turbocharged compression-ignited internal combustion engine, said method comprising:
    02635-1I-DK-P
    DK 2016 70955 A1 supplying pressurized liquid fuel at a first high pressure to a fuel valve (50) of said engine, said fuel valve having an elongated valve housing (52) with a rear end and a front end, said fuel valve (50) having a hollow nozzle (54) with a plurality of nozzle holes (56) connecting the interior (55) of said nozzle (54) to a combustion chamber in a cylinder (1) of said engine, said nozzle (54) comprising a base (46) and an elongated nozzle body, said nozzle (54) being connected with its base (46) to said front end of said elongated valve housing (52), said nozzle (54) having a closed tip (59) with said nozzle holes (56) arranged close to said tip (59), supplying ignition liquid at a second high pressure to said fuel valve (50), said second high pressure being higher than said first high pressure, controlling the injection of the liquid fuel with a displaceable valve needle (61) that cooperates with a seat (69) above said hollow nozzle (54), a fuel chamber (58) being arranged above said seat (69), pressuring said fuel chamber (58) with said liquid fuel, delivering a small continuous flow of ignition liquid to said fuel chamber (58) and allowing said ignition liquid to accumulate above the seat (69) during periods where the axially displaceable valve needle (61) rests on the seat (69) and starting a liquid fuel injection event by lifting said axially displaceable valve needle (61) from
    02635-1I-DK-P
    DK 2016 70955 A1 said seat (69), thereby causing said accumulated ignition liquid to enter the hollow injection nozzle (54) just ahead of the liquid fuel,
    5 or delivering a precisely dosed amount of ignition liquid to said seat (69) when the axially displaceable valve needle (61) has lift, and starting a liquid fuel injection event by lifting said axially displaceable valve needle (61) from said seat (69), thereby causing
    10 said accumulated ignition liquid to enter the hollow injection nozzle (54) simultaneously with the liquid fuel.
    18. A method according to claim 17, wherein said liquid
    15 fuel ignites inside said nozzle (54) with the help of said ignition liquid.
    02635-1I-DK-P
    DK 2016 70955 A1
    DK 2016 70955 A1 i>
    [4] 4/7
    类似技术:
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    同族专利:
    公开号 | 公开日
    DK179213B9|2018-04-16|
    DK179213B1|2018-02-05|
    KR20180062943A|2018-06-11|
    JP2018091334A|2018-06-14|
    JP6472503B2|2019-02-20|
    KR101921490B1|2019-02-13|
    DK201670955A9|2018-04-16|
    EP3330526B1|2019-07-31|
    CN108131229A|2018-06-08|
    CN108131229B|2019-09-06|
    EP3330526A1|2018-06-06|
    RU2674868C1|2018-12-13|
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    EP3070321A1|2015-03-20|2016-09-21|Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland|Fuel valve for injecting a low flashpoint fuel into a combustion chamber of a large self-igniting turbocharged two-stroke internal combustion engine|
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    DK178149B1|2013-10-30|2015-06-29|Man Diesel & Turbo Deutschland|A Fuel Valve for Pilot Oil Injection and for Injecting Gaseous Fuel into the Combustion Chamber of a Self-Igniting Internal Combustion Engine|
    DK178521B1|2014-10-17|2016-05-09|Man Diesel & Turbo Deutschland|A fuel valve for injecting gaseous fuel into a combustion chamber of a self-igniting internal combustion engine, engine, method and use|
    DK178519B1|2014-10-17|2016-05-09|Man Diesel & Turbo Deutschland|A fuel valve for injecting gaseous fuel into a combustion chamber of a self-igniting internal combustion engine and method|
    DK178674B1|2015-03-20|2016-10-24|Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland|Fuel valve for injecting a low flashpoint fuel into a combustion chamber of a large self-igniting turbocharged two-stroke internal combustion engine|CN109372658B|2018-12-10|2020-10-13|大连理工大学|Gas injector of gas engine and working method thereof|
    DK180001B1|2018-12-11|2020-01-15|MAN Energy Solutions|A large two-stroke compression-ignited internal combustion engine with fuel injection system for a low flashpoint fuel and a fuel valve therefore|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DKPA201670955A|DK179213B9|2016-12-01|2016-12-01|A fuel valve for injecting a liquid fuel into a combustion chamber of a large compression-igniting turbocharged two-stroke internal combustion engine|DKPA201670955A| DK179213B9|2016-12-01|2016-12-01|A fuel valve for injecting a liquid fuel into a combustion chamber of a large compression-igniting turbocharged two-stroke internal combustion engine|
    KR1020170157009A| KR101921490B1|2016-12-01|2017-11-23|A fuel valve and method for injecting a liquid fuel into a combustion chamber of large compression-igniting turbocharged two-stroke internal combustion engine|
    EP17203729.3A| EP3330526B1|2016-12-01|2017-11-27|A fuel valve and method for injecting a liquid fuel into a combustion chamber of a large compression-igniting turbocharged two-stroke internal combustion engine field|
    CN201711221989.9A| CN108131229B|2016-12-01|2017-11-29|By the fuel valve of liquid fuel penetrating engine combustion chamber and method and engine|
    RU2017141730A| RU2674868C1|2016-12-01|2017-11-30|Fuel valve and method for injection of liquid fuel in combustion chamber of large two-stroke internal combustion engine with compression combustion|
    JP2017231809A| JP6472503B2|2016-12-01|2017-12-01|Fuel valve for a large-sized turbocharged compression ignition two-stroke internal combustion engine, an internal combustion engine using the same, and a method of operating the engine|
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