DK181318B1 - A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine - Google Patents
A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine Download PDFInfo
- Publication number
- DK181318B1 DK181318B1 DKPA202200135A DKPA202200135A DK181318B1 DK 181318 B1 DK181318 B1 DK 181318B1 DK PA202200135 A DKPA202200135 A DK PA202200135A DK PA202200135 A DKPA202200135 A DK PA202200135A DK 181318 B1 DK181318 B1 DK 181318B1
- Authority
- DK
- Denmark
- Prior art keywords
- fuel
- valve
- nozzle
- flow
- needle
- Prior art date
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 148
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 36
- 239000007787 solid Substances 0.000 claims description 2
- 230000000284 resting effect Effects 0.000 abstract description 6
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 22
- 238000002347 injection Methods 0.000 description 20
- 239000007924 injection Substances 0.000 description 20
- 229910021529 ammonia Inorganic materials 0.000 description 11
- 230000008033 biological extinction Effects 0.000 description 6
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 4
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 description 3
- 229910002092 carbon dioxide Inorganic materials 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 239000010763 heavy fuel oil Substances 0.000 description 2
- WWYNJERNGUHSAO-XUDSTZEESA-N (+)-Norgestrel Chemical compound O=C1CC[C@@H]2[C@H]3CC[C@](CC)([C@](CC4)(O)C#C)[C@@H]4[C@@H]3CCC2=C1 WWYNJERNGUHSAO-XUDSTZEESA-N 0.000 description 1
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- OTMSDBZUPAUEDD-UHFFFAOYSA-N Ethane Chemical compound CC OTMSDBZUPAUEDD-UHFFFAOYSA-N 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 229910001315 Tool steel Inorganic materials 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- -1 for example Substances 0.000 description 1
- 239000000295 fuel oil Substances 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000005431 greenhouse gas Substances 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000010791 quenching Methods 0.000 description 1
- 230000000171 quenching effect Effects 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
- F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
- F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
- F02M51/0642—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto
- F02M51/0653—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto the valve being an elongated body, e.g. a needle valve
- F02M51/0657—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto the valve being an elongated body, e.g. a needle valve the body being hollow and its interior communicating with the fuel flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0203—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels characterised by the type of gaseous fuel
- F02M21/0206—Non-hydrocarbon fuels, e.g. hydrogen, ammonia or carbon monoxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/0248—Injectors
- F02M21/0275—Injectors for in-cylinder direct injection, e.g. injector combined with spark plug
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/28—Details of throttles in fuel-injection apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/008—Means for influencing the flow rate out of or into a control chamber, e.g. depending on the position of the needle
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Described is a fuel valve (1) for a large turbocharged two-stoke uniflow crosshead internal combustion engine, said fuel valve (1) comprising an elongated fuel valve housing (2) with a rear end (3) and a front end (4), a nozzle (5) with at least one bore (7) opening into at least one nozzle hole (9) having a nozzle hole area, said nozzle (5) being arranged at the front end (4) of said housing (2), a fuel channel (11) extending from the rear end (3) towards the front end (4) and being connected to a source of pressurized fuel, an axially displaceable valve needle (12) having a closed position, in which said axially displaceable valve needle (12) is resting on a valve seat (8) preventing fuel from flowing to the nozzle (5), and an open position in which said axially displaceable needle (12) is lifted from said valve seat (8) thereby exposing a valve needle flow area (13) between said needle (12) and said valve seat (8) allowing fuel to flow through the fuel valve (1) to the nozzle hole (9) via a flow path defined by at least the fuel channel (11), the valve needle flow area (13) and the at least one bore (9) in the nozzle (5). The fuel valve (1) is peculiar in that it comprises a flow restriction (20) in said flow path of the fuel.
Description
DK 181318 B1 1
The present invention relates to a fuel valve for a large turbocharged two-stoke uniflow crosshead internal combustion engine, said fuel valve comprising an elongated fuel valve housing with a rear end and a front end, a nozzle with at least one bore opening into at least one nozzle hole having a nozzle hole area, said nozzle being arranged at the front end of said housing, a fuel channel extending from the rear end towards the front end and being connected to a source of pressurized fuel, an axially displaceable valve needle having a closed position, in which said axially displaceable valve needle is resting on a valve seat preventing fuel from flowing to the nozzle, and an open position in which said axially displaceable needle is lifted from said valve seat thereby exposing a valve needle flow area between said needle and said valve seat allowing fuel to flow through the fuel valve to the nozzle hole via a flow path defined by at least the fuel channel, the valve needle flow area and the at least one bore in the nozzle, where said fuel valve comprises a flow restriction in said flow path of the fuel.
Large turbocharged two-stroke uniflow crosshead internal combustion engine are typically used as prime movers in large ocean going ships, such as container ships or in power plants. Very often, these engines are operated with heavy fuel oil or with fuel oil
Recently, there has been a demand for large two-stroke diesel engines to be able to handle alternative types of fuel, such as gaseous fuel, for example, methanol, LPG,
LNG, ethane, ammonia and/or other similar fuels.
Such fuels are relatively clean fuels that result in significantly lower levels of sulfurous components, NOx and CO2 in the exhaust gas when used as fuel for a large low-speed
DK 181318 B1 2 uniflow turbocharged two-stroke internal combustion engine when compared with e.g. using Heavy Fuel Oil as fuel.
However, there are problems associated with using such fuels in a large turbocharged two-stroke uniflow crosshead internal combustion engine. One of those problems is the willingness and predictability of the fuel to self-ignite and both are essential to have under control in such an engine. Therefore, existing large turbocharged two-stroke uniflow crosshead internal combustion engines typically use pilot injection of oil simultaneously with the injection of the gaseous fuel to ensure reliable and properly timed ignition of the gaseous fuel.
Further, these engines are typically provided with two or three fuel valves arranged in each cylinder cover. The fuel valve may be provided with a spring biased axially movable valve needle that acts as a movable valve member. When the pressure of the — fuel exceeds a preset pressure (typically about 350 Bar) the axially movable valve needle is lifted from its valve seat and the fuel is allowed to flow into the combustion chamber via a nozzle at the front of the fuel valve. The fuel valve needle may also be actuated and controlled by external hydraulic or electrical power. — Currently, ammonia enjoys very high interest as fuel for internal combustion engines mainly because it may be produced in an environmental friendly way by use of electricity from renewable energy sources, such as sun, wind and wave energy and because the combustion of ammonia per se takes place without formation of carbon containing greenhouse gases, such as carbon dioxide.
When ammonia is used as fuel for an internal combustion engine, the engine may be operated according to the Otto principle where ammonia fuel is introduced at relatively low pressure during the compression stroke of the piston, or the engine may be operated after the Diesel principle, where the ammonia fuel is injected at high pressure into the combustion chamber when piston is close to top dead center (TDC). During the ammonia fuel injection and combustion phase of the piston cycle the cylinder pressure is undergoing dramatic changes in level both due to compression/expansion of the chamber and due to the combustion taking place.
DK 181318 B1 3
Current fuel injection systems for internal combustion engines being operated according to the Diesel principle all require the fuel injection pressures to be considerably higher than the maximum pressure inside the combustion chamber of the cylinder in order to ensure a steady and well controlled fuel mass rate into the cylinder during injection. The main pressure drop is always located at the nozzle hole, where fuel is injected into the combustion chamber with high velocity. Hence, the injection pressure level together with the effective nozzle area is defining the fuel injection mass rate.
While this is desirable with most fuels, when injecting ammonia into a combustion chamber of a cylinder of an internal combustion engine the injection pressure and velocity may need to be much lower in order to not disturb the combustion and make stabilization of the flame close to a fuel valve or injector possible. Ammonia has a laminar flame velocity that is almost 10 times lower than that of most hydrocarbons, hence quenching/extinction of the flame may happen at even low turbulence levels.
Furthermore, too high velocities in the fuel jet may just sweep/convert a flame downstream with no chance to stabilize itself at a limited lift off length from the nozzle hole exit. It may be seen as blowing out a candle.
The currently existing fuel injection systems are not able to inject fuel at a steady injection rate with low pressures, because the down-stream pressure is varying dramatically during the injection duration. Transient control of the injection pressure (for instance by controlling the hydraulic driving pressure of the booster or the fuel pressure of a common rail system within milliseconds) is not possible.
From WO 2015/091180 A1 (equivalent to JP 2017/507269) and US 2009/0032622 are known fuel valves of the kind mentioned in the introduction. In these known fuel valves the flow restriction is arranged in the flow path upstream of the valve seat. Thus, in these known fuel valves the forces from the fuel medium acting on the valve needle, that need to be counteracted by springs, actuators (electric, hydraulic, etc.) will be affected by the flow restriction or changes of the flow restriction. Hence the demands for actuation forces on and the control of the actuation of the valve needle are dependent of the flow restriction. Further, in these prior art fuel valves opening of the valve needle
DK 181318 B1 4 will immediately result in a steep decrease of pressure acting on the needle, which in turn will require a very large actuation force in order to keep the needle open.
The invention also relates to a large turbocharged two-stoke uniflow crosshead internal combustion engine comprising a fuel valve as described above and claimed in the attached claims.
—Itis an object of the present invention to provide a fuel valve of the kind mentioned in the introduction, where the above mentioned challenges relating to extinction of the flame and the forces from the fuel medium acting on the valve needle are at least significantly reduced. — The foregoing and other objects are achieved by the features of the independent claims.
Further implementation forms are apparent from the dependent claims, the description, and the figures.
According to a first aspect, there is provided a fuel valve for a large turbocharged two- stoke uniflow crosshead internal combustion engine, said fuel valve comprising an elongated fuel valve housing with a rear end and a front end, a nozzle with at least one bore opening into at least one nozzle hole having a nozzle hole area, said nozzle being arranged at the front end of said housing, a fuel channel extending from the rear end towards the front end and being connected to a source of pressurized fuel, an axially displaceable valve needle having a closed position, in which said axially displaceable valve needle is resting on a valve seat preventing fuel from flowing to the nozzle, and an open position in which said axially displaceable needle is lifted from said valve seat thereby exposing a valve needle flow area between said needle and said valve seat allowing fuel to flow through the fuel valve to the nozzle hole via a flow path defined by at least the fuel channel, the valve needle flow area and the at least one bore in the nozzle, where said fuel valve comprises a flow restriction in said flow path of the fuel, and being characterized in that the flow restriction is provided in the flow path between the valve seat and the nozzle hole(s).
DK 181318 B1
Hence, by introducing a flow restriction in the flow path between the valve seat and the nozzle hole(s), hence at a different location than the nozzle hole itself (or nozzle holes themselves) the injection flow rate is determined by the injection pressure and the effective open flow area of the flow restriction, thereby avoiding high exit velocities 5 into the cylinder at the nozzle hole(s). In this way the fuel may be injected into the combustion chamber of a cylinder of an internal combustion engine at a lower injection velocity and thus facilitating a lower risk of extinction of the flame, while still maintaining a high fuel supply pressure in the fuel injection system. The fuel, such as ammonia may thus be injected with a well-controlled mass rate into the cylinder, that eliminates or at least lowers the risk of extinction of the flame. In addition, the forces from the fuel medium acting on the valve needle are not affected by the flow restriction.
The injection system may maintain a high supply pressure by controlling the pressure in a common-rail system or by keeping constant high hydraulic pressure driving booster valves.
The flow restriction should provide an flow area that ensures the correct fuel flow rate given the chosen pressure level. Thus, it is preferred that the flow area of the flow restriction is significantly smaller than the nozzle hole area. In a preferred embodiment of the invention the flow area of the flow restriction is less than 3/4, preferably less than 1/2 and most preferably less than 1/3 of the nozzle hole area. Hence, in this way the fuel may be injected through the nozzle hole at a constant mass rate and velocity independent of the cylinder pressure.
The nozzle may comprise more than one bore opening into at least one nozzle hole. In such embodiment the nozzle holes preferably have equal nozzle hole area. However, a nozzle with more nozzle holes of different areas is conceivable. In another embodiment the nozzle may comprise one bore supplying fuel to all nozzle holes. In embodiments with a nozzle having more nozzle holes it is the total nozzle hole area of all nozzle holes, which has to be compared and sized relative to the flow area of the flow restriction.
DK 181318 B1 6
In one embodiment of the invention, where the flow restriction is provided in the flow path between the valve seat and the nozzle hole, a reduction of the cross sectional area of at least a part of the bore may be provided. In practice such restriction could be provided by introducing a flow restriction insert into the bore extending from valve seat to the nozzle hole. If fuel is delivered to each nozzle hole via an individual bore for each nozzle hole, flow restriction inserts have to be provided in all of the bores, where the flow restriction area of the inserts being smaller than the nozzle hole area of each individual nozzle hole that is supplied with fuel from that bore. — In another embodiment of the invention, where the flow restriction also is provided in the flow path between the valve seat and the nozzle hole(s), the nozzle of the fuel valve only comprises one bore, which one bore supplies fuel to a number of nozzle holes, only one such flow restriction insert will be needed, with a flow restriction area that is smaller than the sum of all nozzle hole flow areas.
In yet another embodiment of the invention, the fuel valve may be a kind of a slide valve, where the nozzle comprises only one bore delivering fuel to a number of nozzle holes and where the valve needle is formed as a cut-off shaft, which extends into the bore and cuts off the nozzle holes, when the valve needle is in its closed position. In such kind of valve, the fuel passes the cut-off shaft via at least one orifice, when the valve needle is in its open position and accordingly, the flow restriction in such valve may be provided in said at least on orifice.
The nozzle holes in the nozzle may be distributed radially and preferably also axially over the nozzle. The nozzle holes may axially be positioned near a tip of the nozzle, which tip preferably is closed. The nozzle holes may preferably be positioned over a relatively narrow range of the perimeter of the nozzle, such as between approximately 50° to 120°. The radial orientation of the nozzle holes may further be directed away from a wall of the combustion chamber defined by a cylinder liner. Further, the nozzle holes may be directed such that they are roughly in the same direction as a direction of a swirl of scavenge air in the combustion chamber caused by the configuration of scavenge ports.
DK 181318 B1 7
The invention will be explained in more details with reference to the example embodiments shown in the drawings, in which:
Fig. 1 shows an embodiment of the fuel valve according to the invention, where the flow restriction is provided in the bore of the nozzle, so the flow area of at least a part of the bore is smaller than the nozzle hole area,
Fig 2 shows an embodiment of the fuel valve according to the invention, where the nozzle comprises only one bore and the flow restriction is provided in said bore, so the flow area of at least a part of the bore is smaller than the nozzle hole area, and
Fig. 3 shows an embodiment of the fuel valve according to the invention, where the — fuel valve is a slide valve, where the nozzle has only one bore and the valve needle is formed as a cut-off shaft, where the flow restriction is provided in an orifice of said cut-off shaft.
In the following detailed description, the fuel valve according to the invention will be described for use in a large two-stroke uniflow scavenged internal combustion engine with crossheads, but it is understood that the internal combustion engine could be of another type.
In Fig. ] is shown an example embodiments of a fuel valve 1 according to the invention.
The example embodiment and the embodiments shown in Fig. 2 and 3 are shown in different cross sections, and therefore are all the same structural elements not shown in all figures, however same reference numbers are used for corresponding elements in the three figures.
The fuel valve 1 shown in Fig. 1 comprises an elongated fuel valve housing 2 with a rear end 3 and a front end 4. At the front end of the housing 2 is a nozzle 5 mounted by
DK 181318 B1 8 means of a retaining element 6. The nozzle 5 comprises, as seen in Fig. 1, five bores 7, which all extend from a valve seat 8 and opening into a nozzle hole 9 for injecting fuel into a combustion chamber 10. The bore 7 has a diameter X defining its flow area and a nozzle hole area is defined by a diameter Y of the nozzle hole 9. The fuel valve 1 further comprises a fuel channel, not seen in Fig. 1, which fuel channel extend from the rear end 3 towards the front end 4 of the fuel valve 1. The fuel channel are connected to a source of pressurized fuel, not shown. Further, the fuel valve comprises a fuel return channel, not shown. In order to control the flow of fuel through the fuel valve 1, it comprises an axially displaceable valve needle 12, which has a closed position, in — which the axially displaceable valve needle 12 is resting on the valve seat 8 preventing fuel from flowing to the nozzle 5, and an open position in which the axially displaceable needle 12 is lifted from the valve seat 8 thereby exposing a valve needle flow area 13 allowing fuel to flow through the fuel valve 1 to the nozzle holes 9. Thus, the fuel valve 1 has a flow path, that is defined by the fuel channel, the valve needle flow area 13 and the bores 7 in the nozzle 5.
The axially displaceable valve needle 12 is slidably received with a narrow clearance in a longitudinal bore in 14 in the elongated valve housing 2. The shown valve needle 12 is provided with a conical section that is shaped to match the valve seat 8. In the — closed position the conical section of the valve needle 12 is resting on the valve seat 8.
The conical section has lift from the valve seat 8 in the open position and the valve needle 12 is resiliently biased towards the closed position by a pre-tensioned helical spring 15. The pre-tensioned helical spring 15 acts on the valve needle 12 and biases the valve needle 12 towards its closed position where the conical section is resting on the valve seat 8. The helical spring 15 is a helical wire spring that is received in a spring chamber 16 in the elongated fuel valve housing 2.
The fuel valves 1 shown in Fig. 2 and 3 comprise basically the same elements as the fuel valve shown in Fig. 1, however with some differences as explained in the following. In Fig. 2 and 3 the nozzle 5 of the fuel valves comprises only one single bore 7, which supplies fuel to all the nozzle holes 9. In addition, the nozzle 5 is shown to be positioned relative to the housing 2 by means of a position pin 22, this applies also for
DK 181318 B1 9 the valve in Fig. 1. Also in these fuel valves, the nozzle 5 is mounted to the housing 2 by means of a retaining element 6, only shown in Fig. 1.
The fuel valve shown in Fig 3 is a slide valve, which is characterized by a special design of the valve needle 12. The valve needle 12 of a slide valve comprises an elongated member, which protrudes into the one single bore 7 and comprises a solid first part 23 and a hollow second part 24 farthest away from the valve seat 8, which hollow part comprises at least one orifice 26 and is open at its free end 25. During operation, when the valve needle is lifted to its open position away from the valve seat 8, the free end 25 of the elongated member is also lifted free of the nozzle holes 9, allowing the fuel to flow in the bore 7 between the elongated member and a wall of the bore 7 down to the orifice(s) 26 and into the hollow part 24 from where it continues to flow out of the open free end 25 and into the nozzle holes 9. — The elongated valve housing 2 and the other components of the fuel valve 1, as well as the nozzle 5 are in preferred embodiments made of steel, such as e.g. tool steel and stainless steel.
The nozzle 5 is, as mentioned, provided with nozzle holes 9, which are distributed radially and preferably also axially over the nozzle 5. The nozzle holes 9 are axially positioned near a tip 17 of the nozzle 5, which tip 17 in the shown embodiments is closed. The nozzle holes 9 are in the presented embodiments distributed over a relatively narrow range of the perimeter of the nozzle 5, such as between approximately 50° to 120° . The radial orientation of the nozzle holes 9 may in such an embodiment be directed away from a wall of the combustion chamber defined by a cylinder liner.
Further, the nozzle holes 9 may be directed such that they are roughly in the same direction as a direction of a swirl of scavenge air in the combustion chamber caused by the configuration of scavenge ports (this swirl is a well-known feature of large two- stroke turbocharged internal combustion engines of the uniflow type).
According to the invention, the fuel valve comprises a flow restriction 20 provided in the flow path between the valve seat (8) and the nozzle hole(s) (9). Hereby, the fuel may be injected into the combustion chamber of a cylinder of an internal combustion
DK 181318 B1 10 engine at a lower injection velocity and thus facilitating a lower risk of extinction of the flame, while still maintaining a high fuel supply pressure in the fuel injection system. The fuel, such as ammonia may thus be injected with a well-controlled mass rate into the cylinder, that eliminates or at least lowers the risk of extinction of the flame.
In the embodiment shown in Fig. 1 the flow restriction 20 is provided in the flow path between the valve seat 8 and the nozzle holes 9. In practice, a reduction of the cross sectional area of at least a part of the bores 7 is provided, however in order to facilitate the manufacture of the nozzle 5, it is preferred, as shown, that the bores 7 over their whole length has the same diameter and that the flow restriction 20 in form of an insert is mounted in each bore 7, where the flow restriction 20 has a flow area that is smaller than the nozzle hole area.
In the embodiment shown in Fig. 2 the flow restriction 20 is also provided in the flow path between the valve seat 8 and the nozzle holes 9. In practice, a reduction of the cross sectional area of a part of the bore 7 is provided by mounting an insert in the bore 7, where the flow restriction 20 in form of the insert has a flow area that is smaller than the total area of the nozzle holes 9.
In the embodiment shown in Fig. 3 the flow restriction 20 is also provided in the flow path between the valve seat 8 and the nozzle holes 9. In this embodiment, the flow restriction 20 is provided in the orifice(s) 26, either by mounting an insert in the orifice(s) 26 or by making the orifice(s) 26 with a smaller diameter ensuring that total — flow area of the orifice(s) 26 is smaller than the total area of the nozzle holes 9.
Claims (10)
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DKPA202200135A DK181318B1 (en) | 2022-02-18 | 2022-02-18 | A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine |
CN202211672536.9A CN116624302A (en) | 2022-02-18 | 2022-12-26 | Fuel valve for large turbocharged two-stroke uniflow crosshead internal combustion engine |
JP2023003437A JP7303400B1 (en) | 2022-02-18 | 2023-01-13 | Fuel valve for large turbocharged 2-stroke uniflow crosshead internal combustion engine |
KR1020230011669A KR102566767B1 (en) | 2022-02-18 | 2023-01-30 | A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine |
EP23155526.9A EP4230860A1 (en) | 2022-02-18 | 2023-02-08 | A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DKPA202200135A DK181318B1 (en) | 2022-02-18 | 2022-02-18 | A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
DK181318B1 true DK181318B1 (en) | 2023-08-10 |
DK202200135A1 DK202200135A1 (en) | 2023-08-10 |
Family
ID=85202243
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
DKPA202200135A DK181318B1 (en) | 2022-02-18 | 2022-02-18 | A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP4230860A1 (en) |
JP (1) | JP7303400B1 (en) |
KR (1) | KR102566767B1 (en) |
CN (1) | CN116624302A (en) |
DK (1) | DK181318B1 (en) |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE482591C (en) * | 1927-04-30 | 1930-02-03 | Werke Kiel Akt Ges Deutsche | Fuel injector for internal combustion engines |
JP3323429B2 (en) * | 1997-11-19 | 2002-09-09 | トヨタ自動車株式会社 | Fuel injection valve for internal combustion engine |
EP1566539B1 (en) * | 2004-02-23 | 2009-01-14 | Wärtsilä Schweiz AG | Fuel injector |
US7690588B2 (en) | 2007-07-31 | 2010-04-06 | Caterpillar Inc. | Fuel injector nozzle with flow restricting device |
EP2239451B1 (en) * | 2009-03-30 | 2011-09-07 | Wärtsilä Switzerland Ltd. | A fuel injector for internal combustion engines |
DE102013001098B3 (en) * | 2013-01-23 | 2014-07-03 | L'orange Gmbh | Fuel injector for use in common-rail system in motor car, has nozzle needle comprising end section that is sealingly retained in through-hole of nozzle tip, where axial bore is extended as blind hole towards near nozzle into end section |
JP5955258B2 (en) * | 2013-03-29 | 2016-07-20 | 三菱重工業株式会社 | Fuel injection device and diesel engine |
GB201322485D0 (en) | 2013-12-19 | 2014-02-05 | Delphi Tech Holding Sarl | Fuel injection nozzle |
JP6080087B2 (en) * | 2014-02-28 | 2017-02-15 | 株式会社デンソー | Fuel injection valve |
GB2548375A (en) * | 2016-03-16 | 2017-09-20 | Delphi Int Operations Luxembourg Sarl | Fuel injector |
DK179281B1 (en) * | 2016-12-13 | 2018-04-03 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | Nozzle for fuel valve for injecting fuel into the cylinders of a large turbocharged two-stroke compression-ignited internal combustion engine |
DK179146B1 (en) * | 2016-12-13 | 2017-12-04 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | Nozzle for fuel valve for injecting fuel into the cylinders of a large turbocharged two-stroke compression-ignited internal combustion engineand and an engine therefore |
GB2560513A (en) * | 2017-03-13 | 2018-09-19 | Ap Moeller Maersk As | Fuel injection system |
-
2022
- 2022-02-18 DK DKPA202200135A patent/DK181318B1/en active IP Right Grant
- 2022-12-26 CN CN202211672536.9A patent/CN116624302A/en active Pending
-
2023
- 2023-01-13 JP JP2023003437A patent/JP7303400B1/en active Active
- 2023-01-30 KR KR1020230011669A patent/KR102566767B1/en active IP Right Grant
- 2023-02-08 EP EP23155526.9A patent/EP4230860A1/en active Pending
Also Published As
Publication number | Publication date |
---|---|
JP7303400B1 (en) | 2023-07-04 |
CN116624302A (en) | 2023-08-22 |
EP4230860A1 (en) | 2023-08-23 |
JP2023121131A (en) | 2023-08-30 |
KR102566767B1 (en) | 2023-08-14 |
DK202200135A1 (en) | 2023-08-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CA1321110C (en) | Intensifier-injector for gaseous fuel for positive displacement engine | |
CA2339504C (en) | Gaseous and liquid fuel injector | |
US6988492B2 (en) | Hydrogen and liquid fuel injection system | |
JP4297181B2 (en) | Injector | |
US8322325B2 (en) | Concurrent injection of liquid and gaseous fuels in an engine | |
KR101930567B1 (en) | A fuel injection unit, a method of operating such and an internal combustion engine | |
US9366195B2 (en) | Fuel injection valve and method of actuating | |
CN203022939U (en) | Dual fuel injection valve device with mixed-type nozzle and for crude oil engine and gas engine | |
RU2619971C2 (en) | Fuel injection valve for gaseous fuel into the combustion chamber of the internal combustion engine with auto-ignition and method | |
JP4441620B2 (en) | Gaseous fuel injection internal combustion engine and method of operating the same | |
RU2618800C2 (en) | Fuel valve and method for gaseous fuel injection into combustion chamber of internal combustion engine | |
US11078827B2 (en) | Pre-chamber ignition system having igniter with gas orifice structured for pre-expanding outgoing combustion gases | |
JP2006046335A (en) | Premixed combustion control device | |
CN112065568B (en) | Pre-chamber ignition system with hydraulically actuated piston | |
US9562497B2 (en) | Engine system having piezo actuated gas injector | |
DK181318B1 (en) | A fuel valve for a large turbocharged two-stroke uniflow crosshead internal combustion engine | |
CN108131219B (en) | Fuel valve for injecting gaseous fuel into a combustion chamber of an engine, and engine | |
JP5065168B2 (en) | engine | |
CN112074660B (en) | Fuel injection device and method for operating a piston engine | |
GB2440595A (en) | Gasoline direct injection i.c. engine | |
JPH07189848A (en) | Combustion method for internal combustion engine | |
KR20230119021A (en) | How 2-Stroke Piston Engines Work, Fuel Injection Systems, Piston Engines and How to Modify 2-Stroke Piston Engines |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PAT | Application published |
Effective date: 20230810 |
|
PME | Patent granted |
Effective date: 20230810 |