CN106460636A - Internal combustion engine and ship equipped with same - Google Patents
Internal combustion engine and ship equipped with same Download PDFInfo
- Publication number
- CN106460636A CN106460636A CN201580013177.8A CN201580013177A CN106460636A CN 106460636 A CN106460636 A CN 106460636A CN 201580013177 A CN201580013177 A CN 201580013177A CN 106460636 A CN106460636 A CN 106460636A
- Authority
- CN
- China
- Prior art keywords
- fuel
- gas
- injection
- valve
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- 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
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
- F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
- F02D19/10—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels peculiar to compression-ignition engines in which the main fuel is gaseous
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
Abstract
An internal combustion engine with improved combustion stability through accelerated mixing of premix gas in a cylinder is provided. This internal combustion engine (1) is equipped with: a piston (13) that moves back and forth inside a cylinder liner (9); a cylinder cover (11) that is disposed on one end of the cylinder liner (9); an exhaust valve (12) that is disposed on the cylinder cover (11); scavenging ports (10) that are disposed on the other end of the cylinder liner (9); and premixing gas valves (30) that are disposed on the cylinder cover (11) and inject fuel gas into the cylinder formed by the cylinder liner (9) and cylinder cover (11). The premixing gas valves (30) are disposed on the cylinder cover (11) and inject the fuel gas at a high pressure toward the piston (13) after the piston (13) has closed the scavenging ports (10).
Description
Technical field
The present invention relates to a kind of use gaseous fuel carries out the internal combustion engine of pre-mixing combustion and possesses the ship of this internal combustion engine.
Background technology
In recent years it is contemplated that the needs of the liquefied gas carrier such as LNG (liquefied natural gas), carry out as marine engine
Dual fuel engine is (hereinafter referred to as " DF electromotor ".) exploitation (with reference to following patent documentations 1 and 2).DF electromotor possesses combustion
Combust the fuel oil pattern of oil and the gaseous fuel pattern of the gaseous fuels such as burning LNG.In addition, in gaseous fuel pattern, as point
The pilot fuel of fire, is usually used fuel oil.
Conventional art document
Patent documentation
Patent documentation 1：No. 5395848 publications of Japanese Patent No.
Patent documentation 2：International Publication No. 2013/183737
The summary of invention
Invention technical task to be solved
Rated speed is used to be set to below 200rpm's as the DF electromotor that the marine engine of liquefied gas carrier uses
Low speed 2 stroke diesel engine.In this DF electromotor, there is the diffusion combustion carrying out gaseous fuel when carrying out gaseous fuel pattern
Diffusion combustion type and the pre-mixing combustion carrying out gaseous fuel pre-mixing combustion type.
The DF electromotor of diffusion combustion type shown in Figure 12.
The DF electromotor 100 of diffusion combustion type possesses cylinder jacket 101 and the piston 103 being moved back and forth in cylinder jacket 101.
The upper end of cylinder jacket 101 is provided with cylinder head 105, and this cylinder head 105 is provided with 107,2 diffusion gaseous fuels of 1 air bleeding valve
Injection valve 109 and 2 fuel valves 111.And, the lower section of cylinder jacket 103 is provided with scavenging port 113.
As shown in figure 12, after closing scavenging port 113 and be also turn off air bleeding valve 107 by piston 103, by piston 103
Rise the air coming in compression cylinder.And, as shown in figure 13, if piston 103 reaches near top dead center, spray from fuel valve 111
Penetrate fuel oil as guide oil, and with this guide oil simultaneously or followed by, spray example from diffusion with gas fuel injection valves 109
As for about 30MPa about high pressure gaseous fuel.Thus, as shown in figure 14, entered in cylinder according to the injection of gaseous fuel
Row diffusion combustion (now, from fuel valve 111 guide oil injection stop), by expansion stroke, piston 103 downwards by
Push.
Possessed based on the diffusion combustion of this gaseous fuel and there is water identical with the diffusion combustion of the fuel oil based on diesel engine
The advantage of flat combustion stability.
But, make use of the diesel engine of the diffusion combustion based on gaseous fuel and the diesel oil of the diffusion combustion that make use of based on fuel oil
Machine is compared, and can reduce by 20～30% about NOx (nitrogen oxides), but due to utilizing diffusion combustion, therefore NOx output according to
So more, it is impossible to meet the Tier III of International Maritime Organization (IMO) defined when using especially as marine engine.Therefore,
There is following problem：It is being suitable for the aerofluxuss confined waters (ECA of above-mentioned Tier III；Emission Control Area) in,
If not carrying out any NOx abatement measure, cannot run.
In order to reduce NOx output it is contemplated that adding SCR (Selective Catalytic Reduction；Selective catalysis
Reduction) etc. exhaust gas treatment device or for reducing EGR (the Exhaust Gas Recirculation of NOx；Exhaust gas recirculatioon) etc.
Attendant equipment, but initial cost and operating cost can be led to increase.
The DF electromotor 120 of pre-mixing combustion type shown in Figure 15.In addition, to illustrated using Figure 12～Figure 14
The DF electromotor 100 identical structure mark same-sign of diffusion combustion type.
Compared with the DF electromotor 100 of the diffusion combustion type shown in the DF electromotor 120 of pre-mixing combustion type and Figure 12 etc., spray gas
The position of the injection valve of fluid fuel is different.Specifically, in the DF electromotor 120 of pre-mixing combustion type, in the side of cylinder jacket 101
The top of portion and scavenging port 113 is provided with 2 premixing gas fuel injection valves 122.
As shown in figure 15, after scavenging port 113 being closed by piston 103, spray from premixing gas fuel injection valves 122
Emanate fluid fuel.From pre-mixed gas Fuelinjection nozzle 122 injection burning gases towards general horizontal direction with e.g., less than
The low pressure of 1.0MPa is sprayed.Thus, premixing imports from scavenging port 113 air and gaseous fuel.And, as Figure 16 institute
Show and rise with piston 103, pre-mixed gas are compressed, if piston 103 reaches near top dead center, spray from fuel valve 111
Guide oil is simultaneously lighted a fire.Thus, as shown in figure 17, carry out pre-mixing combustion based on flame-front propagation in cylinder (now,
Stop from the injection of the guide oil of fuel valve 111), by expansion stroke, piston 103 is pushed downwards.
NOx output, is had based on the pre-mixing combustion of this gaseous fuel low, even and if unfavorable with above-mentioned SCR and EGR
Also the advantage that above-mentioned Tier III can be implemented separately by electromotor.
But, the DF electromotor 120 of pre-mixing combustion type has the generation distinctive premature firing of pre-mixing combustion, detonation etc. extremely
The risk of burning, and have compared with diffusion combustion, the problem of poor combustion stability.
And, the DF electromotor 120 of pre-mixing combustion type be injection low pressure gaseous fuel structure, therefore, gaseous fuel with
The mixing of air (scavenging) is not abundant and mixed gas concentration easily becomes uneven.Known premature firing, detonation etc. are abnormal
Burning easily produces in the position of local gas concentration higher (excess air ratio λ is low), if only spraying the gaseous fuel of low pressure, mixes
Closing gas concentration becomes uneven, therefore, occurs the probability of abnormal combustion to uprise.
In contrast, having disclosed in above-mentioned patent documentation 1, by from the height and position direction being provided with gas spray valve and cylinder
The axially orthogonal direction of body, with low-pressure fuel injection gaseous fuel, will not make gaseous fuel towards cylinder body top, the aerofluxuss becoming focus
Valve and mix with the scavenging importing from scavenging port, thus gaseous fuel can not being set to high pressure and carrying out premixing.But, this is special
It is horizontal direction that injection method described in sharp document 1 there is also due to the injection direction of gaseous fuel, utilization therefore not yet in effect
The top (region shown in symbol A of Figure 15 (b)) of combustion space, and the not sufficient problem of premixing.
Therefore, using in the DF electromotor of pre-mixing combustion, have in order to avoid abnormal combustion have to reduce compression ratio to transport
OK, lead to the problem that the thermal efficiency declines.
And, the operation under the high load capacity of higher Pme (mean effective pressure in cylinder), is more susceptible to abnormal combustion and combustion
Burn stability to decline, therefore, even if reducing geometric compression ratio also as described above to be difficult to heavy-duty service, and then needs are right
Load (i.e. Pme) is limited.Especially, there is when using DF electromotor as marine engine following problem：Above-mentioned being suitable for
It is impossible to carry out heavy-duty service in the ECA of Tier III, and lead to reduce the operation degree of freedom of ship.
The present invention completes in light of this situation, its object is to provide the pre-mixed gas in a kind of promotion cylinder
Mix and to improve the internal combustion engine of combustion stability and to possess the ship of this internal combustion engine.
For solving the means of technical task
The internal combustion engine of the 1st mode of the present invention possesses：Cylinder jacket；Piston, is moved back and forth in this cylinder jacket；Cylinder
Lid, is arranged at a side of described cylinder jacket；Air bleeding valve, is arranged at this cylinder head；Scavenging port, is arranged at the another of described cylinder jacket
One side；And the 1st gas fuel injection valves, it is arranged at described cylinder head, and formed to by described cylinder jacket and described cylinder head
Cylinder injection gaseous fuel as pre-mixing combustion fuel, described 1st gas fuel injection valves are closed to by described piston
This piston after described scavenging port sprays described gaseous fuel.
In 1st mode of the present invention, by the 1st gas fuel injection valves located at cylinder head, close scavenging directed through piston
Piston (for example from above towards lower section) gas injection fuel after mouthful.Closed by piston thereby, it is possible to effectively utilizes and sweep
The piston reciprocating moving direction (such as above-below direction) of the combustion space after QI KOU simultaneously sprays gaseous fuel to entirety, can promote
Enter the mixing of gaseous fuel and oxidant gas.Therefore, it is possible to increase Local Minimum λ that local gas fuel concentration uprises, (λ is
Excess air ratio), by avoiding the abnormal combustions such as premature firing, detonation as far as possible, it is possible to increase combustion stability.And, by
In the abnormal combustions such as premature firing, detonation can be avoided as far as possible, therefore, compared with conventional premixed engine, can subtract
The reduction amount of small reduction ratio, and the reduction of the thermal efficiency can be made to minimize it is also possible in higher Pme (mean effective pressure in cylinder)
High load capacity under run.
As the moment of gas injection fuel, preferably after piston closes scavenging port and gaseous fuel will not be revealed from air bleeding valve
To the scope of its exterior, specifically, for example, more than 140 and below 20degBTDC (BTDC be Before Top Dead
Centre), it is preferably set to more than 100 and below 60degBTDC.In addition, the 1st gas fuel injection valves of the manner and air bleeding valve
Similarly it is arranged at cylinder head, gas injection fuel in the way of away from air bleeding valve, therefore, even if completely close it in air bleeding valve
Front it is also possible to start gaseous fuel injection.Before closing air bleeding valve, so start the injection of gaseous fuel, be then able to ensure that
The time that gaseous fuel is mixed with oxidant gas is more, therefore, it is possible to more uniformly mix.As the moment of exhaust valve closure,
For example, about 90degBTDC.
Period (that is, the period of sustained firing) as gas injection fuel, for example, the load of internal combustion engine is to be set to when 100%
More than 20deg and below 30deg.
When the 1st gas fuel injection valves are provided with the spray orifice of multiple gas injection fuel, as long as the gas from the injection of at least one spray orifice
Fluid fuel is towards the piston closed after scavenging port.
As internal combustion engine, for example, use and from scavenging port, oxidant gas are imported in cylinder, from the 1st gas fuel injection valves by gas
The oxidant gas in cylinder for the fuel injection, the uniflow scavenging formula of the burning gases after air bleeding valve discharges burning.
In the internal combustion engine of the 1st mode of the present invention, the stroke of described piston is cylinder diameter with the ratio of the internal diameter of described cylinder jacket
Stroke ratio can be set to more than 3.
The ultra-long-stroke the use of bore stroke ratio being more than 3.Therefore, the combustion space after scavenging port is closed by piston
Become the shape that the carrying out along piston moves back and forth the lengthwise of direction extension.Therefore, using make use of gas in this diesel engine
During the premixed combustion mode of fuel, it is difficult to make gaseous fuel equably mix with oxidant gas (such as air).
In 1st mode of the present invention, the 1st gas fuel injection valves are arranged at cylinder head, towards the work closed after scavenging port
Plug (for example from above towards lower section) gas injection fuel, even if be therefore ultra-long-stroke it is also possible to effectively utilizes combustion space
Piston reciprocating moving direction (such as above-below direction) and gaseous fuel is sprayed to entirety, gaseous fuel and oxidation can be promoted
The mixing of agent gas.
As the internal combustion engine of the 1st mode of the present invention, using low speed 2 stroke diesel for example being run with specified below 200rpm
Machine, is mainly used in marine engine.
In the internal combustion engine of the 1st mode of the present invention, the pressure of the gaseous fuel spraying from described 1st gas fuel injection valves, with
Absolute pressure can be set to more than 1.0MPa and below 50MPa.
It is set to the high-pressure injection gaseous fuel of more than 1.0MPa and below 50MPa with absolute pressure, therefore, it is possible to further
Promote the mixing with oxidant gas.
As injection pressure, more preferably more than 20MPa and below 30MPa are set to absolute pressure.
In the internal combustion engine of the 1st mode of the present invention, described cylinder head can be provided with to be used to the fuel oil of described cylinder injection fuel oil
Injection valve.
Make when the fuel oil that the fuel oil being arranged at cylinder head is sprayed with injection valve is in the pre-mixing combustion based on gaseous fuel
Use for guide's oil.That is, by being lighted a fire with the fuel oil that injection valve sprays from fuel.
By possessing, the fuel oil being sprayed with injection valve from fuel oil is used with fuel to run the combustion of internal combustion engine as diffusion combustion
Oily pattern (so-called fuel oil specially burns pattern), as possessing the dual fuel engine that fuel oil pattern is with gaseous fuel pattern, (DF sends out
Motivation), internal combustion engine can be used.
When using as DF electromotor, by selecting fuel oil pattern, the higher operation of combustion stability can be carried out.The opposing party
Face, as long as selecting gaseous fuel pattern, then it can be avoided that discharging the SOx from fuel oil, and can reduce the operation of fuel oil pattern
Time and suppress fuel cost.
In the internal combustion engine of the 1st mode of the present invention, described cylinder head is additionally provided with to described cylinder injection gaseous fuel
2nd gas fuel injection valves, described internal combustion engine can possess switching diffusion gas fuel mode and pre-mixed gas fuel mode
Control unit, described diffusion gas fuel mode is burnt using described 2nd gas fuel injection valves, described pre-mixed gas combustion
Material pattern is burnt using described 1st gas fuel injection valves.
By the 2nd gas fuel injection valves to cylinder injection gaseous fuel, burning compared with pre-mixing combustion can be carried out
The high diffusion combustion of stability.When being provided with above-mentioned fuel injection valve, from this fuel injection valve injection fuel oil as based on gas
The guide oil during diffusion combustion of fuel uses.
By switching the 1st gas fuel injection valves and the 2nd gas fuel injection valves, can according to circumstances distinguish use and be premixed
The pre-mixed gas fuel mode of combination burning and the diffusion gas fuel mode being diffused burning.
For example, when using in the region being suitable for aerofluxuss restriction as ECA, select pre-mixing combustion gas mode, can
NOx suppression in aerofluxuss is run below limits value.Thus it is not necessary to be used for removing the pump-down process such as the SCR of NOx
Device, for reducing the attendant equipments such as the EGR of NOx.On the other hand, in the region not being suitable for aerofluxuss restriction, select diffusion
Gaseous fuel pattern, can carry out the higher operation of combustion stability.
From diffusion gas fuel injection valves injection gaseous fuel pressure be set to compress when in-cylinder pressure more than and 50MPa
(absolute pressure) below, is more preferably set to more than 10MPa and below 30MPa with absolute pressure.
In the internal combustion engine of the 1st mode of the present invention, described control unit can switch to described premixed gas fluid fuel mould just
Increase the gaseous fuel quantity from the 1st gas fuel injection valves injection, directly in the combustion stroke in initial circulation after formula
Concentration to the gaseous fuel burning completely becoming from described 1st gas fuel injection valves injection.
From be diffused burn diffusion gas fuel mode, as diffusion fuel oil pattern do not use pre-mixed gas to fire
When the pattern switching of material is the pre-mixed gas fuel mode carrying out pre-mixing combustion, it is carried out as follows work.For example from being expanded
When the diffusion gas fuel mode of scattered burning switches to pre-mixed gas fuel mode, reduce and spray from the 2nd gas fuel injection valves
The gaseous fuel penetrated, and increase the gaseous fuel from the 1st gas fuel injection valves injection.That is, from diffusion gas fuel mode
Switch to during pre-mixed gas fuel mode it is contemplated that will spray from the 1st gas fuel injection valves in all gas fuel of injection
The ratio of the gaseous fuel penetrated is premixing ratio, and to be gradually increased to 100% through multiple circulations from 0% (only diffusion combustion) (only pre-
Mixed combustion).Now, if premixing ratio is gradually increased through multiple circulations, in the circulation of premixing ratio less initial stage
When, less and premixing concentration is relatively low from the gaseous fuel quantity of the 1st gas fuel injection valves injection, it is therefore possible to gas cannot be made
Fluid fuel burns completely and leads to unburned gaseous fuel to be discharged from air bleeding valve.
Therefore, in the 1st mode of the present invention, just after diffusion gas fuel mode switches to pre-mixed gas fuel mode
Initial circulation in combustion stroke in increase gaseous fuel quantity from the 1st gas fuel injection valves injection, until become gas
The concentration of fluid fuel burning completely, thus, it is possible to prevent when diffusion gas fuel mode switches to pre-mixed gas fuel mode
Unburned gas is discharged from air bleeding valve.
For example, the premixing ratio after switching is set to more than 40% and less than 60%.Preferably in firm switching | after be set to 40%
Above and after less than 60% premixing ratio, it is gradually increased premixing ratio through follow-up multiple circulations.
In the internal combustion engine of the 1st mode of the present invention, can be from described 1st gas fuel injection valves gas injection fuel, and from described
2nd gas spray valve gas injection fuel is as pre-mixed fuel.
As pre-mixed fuel and combustion space can be effectively utilized from the 1st gas fuel injection valves gas injection fuel
Interior piston reciprocating moving direction makes gaseous fuel equably mix with oxidant gas.But, because the 1st gaseous fuel sprays
Valve is arranged at cylinder head, therefore, it is possible to the mixing of the zone gas fuel of the cylinder head side in cylinder is relatively poor.The opposing party
Face, in the 2nd gas fuel injection valves, piston to cylinder head side rise when spray fuel carry out diffusion combustion, therefore, gas fires
The injection direction of material towards the region (specifically, be upper area) in cylinder of the cylinder head side in cylinder, therefore, it is possible to pass through
2nd gas fuel injection valves promote the mixing in the cylinder head side region in cylinder.
Therefore, in the 1st mode of the present invention, from the 1st gas fuel injection valves gas injection fuel as pre-mixed fuel, enter
And, from the 2nd gas fuel injection valves gas injection fuel as pre-mixed fuel, thus, it is possible to overall uniform to combustion space
Ground is mixed.
Preferably after the 1st gas fuel injection valves gas injection fuel, make from the 2nd gas fuel injection valves gas injection fuel
For pre-mixed fuel, promote further by gas injection fuel successively to mix.
2nd mode of the present invention is the ship using any of the above-described internal combustion engine as marine engine.
In 2nd mode of the present invention, by using above-mentioned internal combustion engine, as avoid premature firing, detonation etc. abnormal as possible
Burning, can be carried out based on the thermal efficiency is excellent and pre-mixing combustion that be also capable of the gaseous fuel of heavy-duty service, therefore, it is possible to
Realize energy saving and the excellent ship of environmental performance.
Invention effect
According to the present invention, by avoiding the abnormal combustions such as premature firing, detonation as far as possible, it is possible to increase combustion stability.
Brief description
Fig. 1 is the overall structure figure of the internal combustion engine representing one embodiment of the present invention.
Fig. 2 is the schematic diagram of the structure of cylinder inner periphery comprising the cylinder jacket shown in Fig. 1, represents injection premixed gas fluid fuel
State, Fig. 2 (a) is top view, and Fig. 2 (b) is longitudinal section.
Fig. 3 is schematic diagram corresponding with Fig. 2, represents the fired state based on guide oil, Fig. 3 (a) is top view, and Fig. 3 (b) is vertical
Sectional view.
Fig. 4 is schematic diagram corresponding with Fig. 2, represents pre-mixing combustion state, Fig. 4 (a) is top view, and Fig. 4 (b) is that vertical profile regards
Figure.
Fig. 5 is schematic diagram corresponding with Fig. 2, represents the stroke of compressed air, Fig. 5 (a) is top view, and Fig. 5 (b) is that vertical profile regards
Figure.
Fig. 6 is schematic diagram corresponding with Fig. 2, represents the spray regime of fired state based on guide oil and diffusion gas fuel,
Fig. 6 (a) is top view, and Fig. 6 (b) is longitudinal section.
Fig. 7 is schematic diagram corresponding with Fig. 2, and Fig. 7 (a) is top view, and Fig. 7 (b) is longitudinal section.
Fig. 8 is the schematic isometric of of the injection direction representing the gaseous fuel from pre-mixed gas valve.
Fig. 9 is the schematic isometric of another of the injection direction representing the gaseous fuel from pre-mixed gas valve.
Figure 10 is the schematic isometric of another of the injection direction representing the gaseous fuel from pre-mixed gas valve.
Figure 11 is the schematic isometric of another of the injection direction representing the gaseous fuel from pre-mixed gas valve.
Figure 12 is the stroke of the air of DF electromotor representing compression diffusion combustion type, and Figure 12 (a) is top view, and Figure 12 (b) is
Longitudinal section.
Figure 13 is the fired state of the guide oil representing the DF electromotor based on diffusion combustion type, and Figure 13 (a) is top view, Figure 13
B () is longitudinal section.
Figure 14 is the diffusion combustion state of the gaseous fuel representing the DF electromotor based on diffusion combustion type, and Figure 14 (a) is to overlook
Figure, Figure 14 (b) is longitudinal section.
Figure 15 is the state of the premixed gas fluid fuel of DF electromotor representing injection pre-mixing combustion type, and Figure 15 (a) is to overlook
Figure, Figure 15 (b) is longitudinal section.
Figure 16 is the fired state of the guide oil representing the DF electromotor based on pre-mixing combustion type, and Figure 16 (a) is top view, figure
16 (b) is longitudinal section.
Figure 17 is the pre-mixing combustion state of the DF electromotor representing pre-mixing combustion type, and Figure 17 (a) is top view, Figure 17 (b)
It is longitudinal section.
Specific embodiment
Hereinafter, refer to the attached drawing illustrates to embodiment involved in the present invention.
The summary of the crosshead type diesel engine (internal combustion engine) 1 involved by one embodiment of the present invention shown in Fig. 1.Show in Fig. 1
The diesel engine 1 going out is the direct current of low speed 2 stroke 1 circulation for example using as the marine engine of the liquefied gas carriers such as LNG ship
Scavenging mode.
Diesel engine 1 possesses underlying platen 3, the framework 5 being arranged on platen 3 and is arranged at the big envelope on framework 5
7.These platens 3, framework 5 and big envelope 7 are fastened and fixed by vertically extending multiple turnbuckles (not shown)
Integral.
Big envelope 7 is provided with cylinder jacket 9, and the lower end side of cylinder jacket 9 is formed with multiple scavenging ports 10.The upper end of cylinder jacket 9 sets
There is cylinder head 11.Cylinder head 11 is provided with air bleeding valve 12.So, employ the scavenging port from the lower end side being arranged at cylinder jacket 9
10 air are imported in cylinder from below as scavenging, and the air bleeding valve 12 from the top in cylinder discharges the direct current of burning and gas-exhausting
Scavenging mode.
After the aerofluxuss that air bleeding valve 12 is discharged gather exhaust manifold 14, it is sent to supercharger 16.In supercharger 16,
By the aerofluxuss being imported into, exhaust driven gas turbine (not shown) is rotated, and thus, coaxially connected compressor (not shown) is carried out
Rotation.The air that compressor compresses are externally introduced, and it is directed to scavenging discrimination after being cooled down by air cooler 18
Pipe 20.The compressed air being directed to scavenging manifold 20 is directed to above-mentioned scavenging port 10.
It is provided with the piston 13 that can be moved back and forth in the space being formed by cylinder jacket 9 and cylinder head 11.Piston rod 15
Upper end can be rotatably mounted to the lower end of piston 13.
In the diesel engine 1 of present embodiment, the ratio of the stroke and the internal diameter of cylinder jacket 9 that are set to piston 13 is bore stroke ratio is 3
Above ultra-long-stroke.
Platen 3 is set to crankcase, and is provided with bent axle 17.It is passed to the propulsion of ship from the rotation output of bent axle 17 output
Use propeller.The lower end of pitman 19 can be rotationally connected with the upper end of bent axle 17.
Framework 5 is provided with the crosshead 21 that can rotationally connect piston rod 15 and pitman 19.That is, under piston rod 15
The upper end of end and pitman 19 is connected to crosshead 21.Vertically extending pair of sliding plate 23 is to be fixed on framework 5 side
State be arranged at the both sides (in Fig. 1 be left and right) of crosshead 21.
The structure of the cylinder inner periphery of diesel engine 1 is schematically shown in Fig. 2.As shown in Fig. 2 cylinder head 11 is provided with conduct
The premixing of the 1st gas fuel injection valves gas fuel injection valves are (hereinafter referred to as " pre-mixed gas valve ".) 30, as the 2nd
The diffusion of gas fuel injection valves gas fuel injection valves are (hereinafter referred to as " diffusion gas valve ".) 32 and fuel injection valve (with
Down referred to as " fuel valve ".)34.
As shown in Fig. 2 (a), outer circumferential side during top view cylinder head 11 is provided with 2 pre-mixed gas valves 30.2 premixs
Close gas trap 30 and be configured at the mutually opposing position in center (i.e. the center of air bleeding valve 12) across cylinder head 11.In addition, premix
The quantity closing gas trap 30 only exemplifies 2, can be 1 or more than 3.
Pre-mixed gas valve 30 is connected to gaseous fuel feed source (not shown), by gaseous fuel with high-pressure injection to by gas
In the cylinder of cylinder sleeve 9 and cylinder head 11 formation.As gaseous fuel, using hydrocarbon gas such as the LNG gasifying.
From the gas jet pressure of pre-mixed gas valve 30, more than 1.0MPa and below 50MPa are set to absolute pressure,
Preferably more than 20MPa and below 30MPa are set to absolute pressure.Be arranged at the front end of pre-mixed gas valve 30 nozzle be provided with many
Individual spray orifice, gaseous fuel sprays to cylinder from each spray orifice.For example, in the present embodiment shown in Fig. 2 (b), gaseous fuel is shown
The state sprayed respectively from 4 spray orifices.As shown in Fig. 2 (b), it is set to from the direction of the gaseous fuel of pre-mixed gas valve 30 injection
The direction of piston 13 is more specifically the top of piston 13 closed after scavenging port 10 directed through piston 13 is piston 13
The direction of the top surface gas injection fuel being set to circle of upper end.
In addition, in pre-mixed gas valve 30, if with from least one spray orifice to the side of the direction gas injection fuel of piston 13
Formula arranges each spray orifice, need not be arranged to the direction gas injection fuel to piston 13 for all of spray orifice.
Pre-mixed gas valve 30 makes diesel engine 1 start when working by pre-mixing combustion, in the expansion based on gaseous fuel
Dissipate burning operation and the diffusion combustion based on fuel oil does not start when running and stops.By the instruction from control unit (not shown)
Carry out startup and the stopping of pre-mixed gas valve 30.
The time for spraying of pre-mixed gas valve 30 is controlled by control unit (not shown), and being set to gaseous fuel will not be from row
The scope that air valve 12 is revealed to its exterior, specifically, for example, is set to more than 140 and below 20degBTDC (BTDC：
Before Top Dead Centre), it is preferably set to more than 100 and below 60degBTDC, here, closing as air bleeding valve 12
Moment, be for example set to about 90degBTDC.
Period (i.e. the period of sustained firing gaseous fuel) as gas injection fuel, the such as load of diesel engine 1 are 100%
When be set to more than 20deg and below 30deg.
As shown in Fig. 2 (a), outer circumferential side during top view cylinder head 11 is provided with 2 diffusion gas valves 32.2 diffusion gas
Body valve 32 is configured at the mutually opposing position in center (i.e. the center of air bleeding valve 12) across cylinder head 11.In present embodiment,
Each diffusion gas valve 32 is configured at the position circumferentially deviateing predetermined angular with respect to pre-mixed gas valve 30, as long as diffusion gas
Valve 32 and pre-mixed gas valve 30 are configured in cylinder head 11.In addition, the quantity of diffusion gas valve 32 only exemplifies 2,
Can be 1 or more than 3, but be set to identical with the quantity of fuel valve 34.
Pre-mixed gas valve 30 is connected to gaseous fuel feed source (not shown), is formed to by cylinder jacket 9 and cylinder head 11
Cylinder injection gaseous fuel.As gaseous fuel, using hydrocarbon gas such as the LNG gasifying in the same manner as diffusion gas valve 32.
It is higher than the air (scavenging) after being compressed by piston 13 from the gas jet pressure of diffusion gas valve 32
Pressure and be set to below 50MPa, for example, be set to more than 10MPa and below 30MPa with absolute pressure.It is arranged at diffusion gas valve 32
The nozzle of front end be provided with multiple spray orifices, gaseous fuel sprays to cylinder from each spray orifice.For example, this embodiment party shown in Fig. 7 (b)
In formula, the state that gaseous fuel sprays respectively from 4 spray orifices is shown.As shown in Fig. 7 (b), from the gas of diffusion gas valve 32 injection
The direction that the direction of fluid fuel is set to horizontal direction or is slightly toward lower section from horizontal direction, and it is set to the top not towards piston 13
The direction in portion, so that piston 13 rises near top dead center and is diffused burning in the combustion space narrowing.
Diffusion gas valve 32 makes diesel engine 1 start when working by diffusion combustion, in the premixing based on gaseous fuel
Do not start and stop when burning runs, the diffusion combustion based on fuel oil runs.Entered by the instruction from control unit (not shown)
The startup of row diffusion gas valve 32 and stopping.In addition, using diffusion gas valve 32 as the gas trap of pre-mixing combustion use when,
Sometimes start (for example with reference to Figure 11) when pre-mixing combustion runs.
The period (i.e. period of sustained firing) of diffusion gas valve 32 gas injection fuel passes through control unit quilt (not shown)
Control, the such as load of diesel engine 1 is to be set to more than 20deg and below 30deg when 100%.
As shown in Fig. 2 (a), during top view cylinder head 11, in the outer circumferential side of air bleeding valve 12 and pre-mixed gas valve 30 and
The inner circumferential side of diffusion gas valve 32 is provided with 2 fuel valves 34.2 fuel valves 34 are configured at (to be arranged across the center of cylinder head 11
The center of air valve 12) mutually opposing position.But, each fuel valve 34 is configured at respect to diffusion gas valve 32 and premixed gas
Body valve 30 circumferentially deviates the position of predetermined angular.In addition, the quantity of fuel valve 34 only exemplifies 2, can be 1, also with
For more than 3.As long as and, the outer circumferential side of air bleeding valve 12, then may not be pre-mixed gas valve 30 and diffusion gas valve
32 inner circumferential side.
Fuel valve 34 is connected to fuel delivery source (not shown), to the cylinder injection being formed by cylinder jacket 9 and cylinder head 11
Fuel oil.As fuel oil, for example, can use the heavy oil such as C heavy oil.
The pressure of the air (scavenging) after the injection pressure of fuel valve 34 is set higher than compressing by piston 13, example
As more than 30MPa and below 80MPa are set to absolute pressure.The nozzle being arranged at the front end of fuel valve 34 is provided with multiple spray orifices,
Fuel oil sprays to cylinder from each spray orifice.For example, in the present embodiment shown in Fig. 3 (b), illustrate that fuel oil sprays respectively from 4 spray orifices
The state penetrated.As shown in Fig. 3 (b), it is set to horizontal direction or from horizontal direction somewhat from the direction of the fuel oil of fuel valve 34 injection
Direction downward, and be set to the direction at the top not towards piston 13 so that piston 13 rise near top dead center and
Lighted a fire or diffusion combustion in the combustion space narrowing.
Fuel valve 34 is by making diesel engine 1 spray the combustion for diffusion combustion when working based on the diffusion combustion of fuel oil
The mode of oil is operated (i.e. fuel oil specially burns operation), and, runs in the pre-mixing combustion based on gaseous fuel and be based on gas
When the diffusion combustion of fluid fuel runs, it is operated in the way of the guide oil of jet ignition.By from control (not shown)
The instruction in portion processed carries out the work of fuel valve 34.
Then, the mode of operation of the diesel engine 1 of said structure is illustrated.Have as follows as mode of operation：Mainly make
With pre-mixed gas valve 30, the pre-mixed gas fuel mode that fuel valve 34 is used as guide；Main use spreads gas
Body valve 32, the diffusion gas fuel mode that fuel valve 34 is used as guide；And the diffusion combustion exclusively with fuel valve 34
Oily pattern (i.e. fuel oil specially burns pattern).
Pre-mixed gas fuel mode is less due to NOx output, and therefore such as ship uses when navigating by water in ECA.
The combustion stability of diffusion gas fuel mode is higher than pre-mixed gas fuel mode, and another fermentation, with pre-mixed gas
It is more that fuel mode compares NOx yield, and therefore such as ship uses when navigating by water outside ECA.And, diffusion gas fuel mode
As long as even if in the scope less than NOx limit amount and in the stipulated time in ECA, then can require the combustion stability epoch
Use for pre-mixed gas fuel mode.
With using compared with during gaseous fuel, the SOx from fuel oil produces more diffusion fuel oil pattern, therefore for example discharges in SOx
When limiting relatively loose marine site navigation, use fuel oil more preferable when requiring higher combustion stability or compared to gaseous fuel
When use.
[pre-mixed gas fuel mode]
Using Fig. 2～Fig. 4, pre-mixed gas fuel mode is illustrated.
As shown in Fig. 2 closing in air bleeding valve 12, and then piston 13 closes the initial stage of the compression stroke after scavenging port 10, passes through
Control unit instruction from pre-mixed gas valve 30 towards the top jet of piston 13 with absolute pressure as 1.0MPa more than and 50MPa
Hereinafter, more than preferably with absolute pressure as 20MPa and the high pressure of below 30MPa gaseous fuel.In addition, in pre-mixed gas combustion
In material pattern, diffusion gas valve 32 cuts out.But, as shown in figure 11, sometimes and with diffusion gas valve 32.
As the time for spraying of the gaseous fuel from pre-mixed gas valve 30, after piston 13 closes scavenging port 10 and
Gaseous fuel will not from air bleeding valve 12 to its exterior reveal in the range of select, such as more than 140 and 20degBTDC with
Under, select preferably more than 100 and between below 60degBTDC.Now, the moment that air bleeding valve 12 is closed is about 90degBTDC.
Gaseous fuel is for example set to when the load of internal combustion engine is 100% from the injection period of pre-mixed gas valve 30 sustained firing
More than 20deg and below 30deg.
The top jet of the cylinder head 11 from top for the pre-mixed gas valve 30 piston 13 downward, therefore, it is possible to have
Effect ground using the combustion space being set to lengthwise closed by piston 13 after scavenging port 10 long side direction and by gaseous fuel
Spray to entirety, gaseous fuel and air (scavenging can be promoted；Oxidant gas) mixing.Especially, the diesel oil of present embodiment
Machine 1 is set to ultra-long-stroke, and the mixing of the gaseous fuel injection therefore based on long side direction is effective.
By from the gaseous fuel that pre-mixed gas valve 30 sprays in cylinder in formed pre-mixed gas after, piston 13 to
Top is mobile and compresses pre-mixed gas.And if, as shown in figure 3, reaching near top dead center, spraying guide from fuel valve 34
Oil is simultaneously lighted a fire.The flame being formed by this igniting carries out pre-mixing combustion while propagation in premixed gas body, such as Fig. 4
Shown, burnt and expansion stroke (now, the injection from the guide oil of fuel valve 34 stops), piston 13 moves downwards
Dynamic.
[diffusion gas fuel mode]
Using Fig. 5～Fig. 7, diffusion gas fuel mode is illustrated.
As shown in figure 5, closing in air bleeding valve 12, so piston 13 close scavenging port 10 after compression stroke in, instrument compression from
The air that scavenging port 10 imports.And if, as shown in fig. 6, piston 13 reaches near top dead center, spraying fuel oil from fuel valve 34
As guide oil, and with in-cylinder pressure simultaneously or followed by when diffusion gas valve 32 jet compression for this guide oil more than
And 50MPa (absolute pressure) is below, more preferably with absolute pressure as 10MPa more than and the high pressure of below 30MPa gaseous fuel.
Thus, as shown in fig. 7, being diffused burning in cylinder according to the injection of gaseous fuel (now, from the guide of fuel valve 34
The injection of oil stops), by expansion stroke, piston 13 is pushed downwards.
In addition, in diffusion gas fuel mode, pre-mixed gas valve 30 cuts out all the time.
[diffusion fuel oil pattern]
With regard to diffusion fuel oil pattern (i.e. fuel oil specially burns pattern), although not shown, but with employ the diffusion combustion phase of general fuel oil
With.Specifically, close air bleeding valve 12 and the rising with piston 13 carries out air compression, near top dead center from fuel valve simultaneously
34 with high-pressure injection fuel oil and carry out diffusion combustion, by making piston 13 decline based on the expansion stroke of this diffusion combustion.
So, by possessing diffusion fuel oil pattern, be capable of diesel engine 1 as with employ running of gaseous fuel
Dual fuel engine (DF electromotor).
In addition, in diffusion fuel oil pattern, pre-mixed gas valve 30 and diffusion gas valve 32 are closed all the time.
[premixing interim process control]
The diesel engine 1 of present embodiment be also equipped with from diffusion gas fuel mode or diffusion fuel oil mode transition to premixed gas
The premixing interim process control carrying out during fluid fuel pattern.
When the diffusion gas fuel mode using gaseous fuel switches to pre-mixed gas fuel mode, reduce from diffusion
The gaseous fuel of gas spray valve 32 injection, and increase the gaseous fuel from pre-mixed gas valve 30 injection.That is, from diffusion gas
When fluid fuel pattern switching is pre-mixed gas fuel mode, will spray from pre-mixed gas valve 30 in all gas fuel of injection
The ratio of the gaseous fuel penetrated is premixing ratio from 0%, and the diffusion gas fuel mode of diffusion combustion (only) is gradually increased to
The 100% pre-mixed gas fuel mode of pre-mixing combustion (only).Now, by the premixing interim process control based on control unit,
In the combustion stroke the just initial circulation after diffusion gas fuel mode switches to pre-mixed gas fuel mode,
Increase the gaseous fuel quantity from pre-mixed gas valve 30 injection and disposably improve premixing ratio, until becoming from premixed gas
The concentration of the gaseous fuel burning completely of body valve 30 injection.Specifically, in the initial circulation in switch mode, will premix
Composition and division in a proportion example is from 0% disposable improve to more than 40% and less than 60%.And, in the initial circulation after firm switch mode
After being set to more than 40% and less than 60% premixing ratio, in follow-up multiple circulations, it is gradually increased premixing ratio.
Thus, when diffusion gas fuel mode switches to pre-mixed gas fuel mode, carried out pre- by initial circulation
The burning completely of fuel combination, is prevented from unburned gas and discharges from air bleeding valve.That is, if through multiple after firm switch mode
Premixing ratio is gradually increased by circulation from 0%, then be prevented from the premixing ratio less initial stage is circulated from premixing
Gas trap 30 injection gaseous fuel quantity is less and premixing concentration is too low and gaseous fuel cannot be made to burn completely, thus leading to
Discharge the unfavorable condition that unburned gaseous fuel is hydrocarbon (HC) from air bleeding valve 12.
And, when the diffusion fuel oil pattern switching employing fuel oil is pre-mixed gas fuel mode, it is also carried out identical
Control.That is, when spreading fuel oil pattern switching for mixed fuel pattern, reduce the fuel oil from fuel valve 34 injection, and
And increase the gaseous fuel from pre-mixed gas valve 30 injection.That is, from diffusion fuel oil pattern switching be premixed gas fluid fuel mould
During formula, the caloric value ratio of the gaseous fuel spraying from pre-mixed gas valve 30 in whole fuel of injection can be premixing
The ratio diffusion fuel oil pattern of diffusion combustion (only) (pre-mixed gas combustion of only pre-mixing combustion that is gradually increased to 100% from 0%
Material pattern).Now, by the premixing interim process control based on control unit, just from diffusion fuel oil pattern switching be premixed gas
In the combustion stroke in initial circulation after fluid fuel pattern, increase the gaseous fuel quantity from pre-mixed gas valve 30 injection
And disposably improve premixing ratio, until become the concentration of the gaseous fuel burning completely from pre-mixed gas valve 30 injection.
Specifically, in the initial circulation in switch mode, by premixing ratio from 0% disposable raising to more than 40% and
Less than 60%.And, it is set to more than 40% and less than 60% premix ratio in the initial circulation after firm switch mode
After example, in follow-up multiple circulations, it is gradually increased premixing ratio.
Thus, when spreading fuel oil pattern switching for pre-mixed gas fuel mode, premixing is carried out by initial circulation
The burning completely of fuel, is prevented from unburned gas and discharges from air bleeding valve.That is, if through multiple circulations after firm switch mode
Premixing ratio is gradually increased from 0%, then it can be avoided that the premixing ratio less initial stage circulation in from pre-mixed gas
Valve 30 injection gaseous fuel quantity is less and premixing concentration is too low and gaseous fuel cannot be made to burn completely, thus leading to from row
Air valve 12 discharges the unfavorable condition that unburned gaseous fuel is hydrocarbon (HC).
[gas fuel injection mode]
Then, the injection direction of the gaseous fuel that pre-mixed gas fuel mode is sprayed from pre-mixed gas valve 30 is said
Bright.The top jet of the piston 13 after the gaseous fuel of pre-mixed gas valve 30 injection closes scavenging port 10 towards piston 13
At least a portion gaseous fuel, but have various modes as described below.Which kind of pattern to be according to the actual bavin adopting using
Shape of oil machine 1 etc. and suitably determine.
In jet mode shown in Fig. 8, the gas that sprays from all spray orifices of pre-mixed gas valve 30 (being 4 Fig. 8)
Fuel is towards the top jet of piston 13.In addition, only illustrating the spray regime of the pre-mixed gas valve 30 from left side in Fig. 8,
But the pre-mixed gas valve 30 from right side similarly sprays from all spray orifices towards the top surface of piston 13 in the identical moment
Emanate fluid fuel.The direction of gas injection fuel is set to the direction of the eddy flow direction SW along the air importing from scavenging port 10, with
Mode with rotational flow air is sprayed.
Variation as Fig. 8 is it is also possible to be set to difference by the moment of the pre-mixed gas valve 30 gas injection fuel from left and right.
Thereby, it is possible to become the moment spray combustion gas respectively of different piston positions in the rising with piston 13, therefore can
Enough promote the mixing of gaseous fuel.
And, the injection pressure when the pre-mixed gas valve 30 gas injection fuel of left and right can also be set to difference.Thus,
The in-position of the gaseous fuel of pre-mixed gas valve 30 injection from left and right can be adjusted, and the mixed of gaseous fuel can be promoted
Close.
And, the direction of the gaseous fuel spraying from pre-mixed gas valve 30 can also be set to the eddy flow direction SW phase with air
Anti- direction, promotes the mixing of gaseous fuel.
In jet mode shown in Fig. 9, the direction of the gaseous fuel spraying from the pre-mixed gas valve 30 of left and right is set to
Different on long side direction.Long side direction thereby, it is possible to be efficiently used the combustion space being set to lengthwise go forward side by side circulation of qi promoting body combustion
The mixing of material.As change gaseous fuel injection direction method it is also possible to change spray orifice direction, even if for identical spray
The direction in hole also can be realized by making the diameter of spray orifice pre-mixed gas valve 30 difference in left and right.
The moment of the pre-mixed gas valve 30 gas injection fuel from left and right uses the moment of the good mixing of gaseous fuel, permissible
For mutually in the same time or not in the same time.
And, the direction of the good mixing of gaseous fuel is used from the direction of pre-mixed gas valve 30 gas injection fuel, permissible
It is the direction of eddy flow direction SW or the opposite to that direction along air.
In jet mode shown in Figure 10, by a part of spray orifice in multiple spray orifices towards piston 13 top, other
Spray orifice is in the way of than this right spray orifice more up side towards the direction tilting in the horizontal direction.Thereby, it is possible to be efficiently used
The long side direction being set to the combustion space of lengthwise carries out the mixing of gaseous fuel.In addition, only illustrating pre- from left side in Figure 10
The spray regime of mixed gas valve 30, but towards the axis with cylinder jacket 9 in the same manner as the pre-mixed gas valve 30 from right side
Symmetrical direction gas injection fuel.The spray orifice tilting in the horizontal direction with regard to the top not towards piston 13, can be set to little
Diameter in the spray orifice at the top towards piston 13.This is because, from the spray orifice gas injection fuel tilting in the horizontal direction
The air becoming blending objects in region is relatively fewer.
The moment of the pre-mixed gas valve 30 gas injection fuel from left and right uses the moment of the good mixing of gaseous fuel, permissible
It is mutually in the same time or not in the same time.
And, the direction of the good mixing of gaseous fuel is used from the direction of pre-mixed gas valve 30 gas injection fuel, permissible
It is the direction of eddy flow direction SW or the opposite to that direction along air.
In jet mode as shown in figure 11, except pre-mixed gas valve 30, also using diffusion gas valve 32.As premix
Close the jet mode of gas trap 30, can be using any one pattern in above-mentioned Fig. 8～Figure 10.Diffusion gas valve 32 is that piston 13 rises
To spray fuel during cylinder head 11 side and carry out lighting a fire, the valve of diffusion combustion, therefore, the injection direction of gaseous fuel is towards in cylinder
Cylinder head 11 side region (the specifically upper area in cylinder).Using the injection direction of this diffusion gas valve 32,
Also using diffusion gas valve 32 during pre-mixed gas fuel mode, thus, it is possible to promote the upper area of cylinder head 11 side in cylinder
Mixing.
With regard to time for spraying, pre-mixed gas valve 30 and diffusion gas valve 32 can be made to spray it is also possible to make premix first simultaneously
After closing gas trap 30 injection, the moment rising to assigned position in piston 13 makes diffusion gas valve 32 spray.So, by from
Pre-mixed gas valve 30 and diffusion gas valve 32 gas injection fuel successively, be capable of being suitable for movement according to piston 13 and
The admixture of the shape of combustion space of change.
As described above, according to the diesel engine 1 of present embodiment, following effect fruit can be played.
Pre-mixed gas valve 30 is arranged at cylinder head 11, closes piston 13 top after scavenging port 10 directed through piston 13
And gas injection fuel from the top to the bottom.Thereby, it is possible to effectively utilize the combustion closed after scavenging port 10 by piston 13
Burn the piston reciprocating moving direction in space and spray gaseous fuel to entirety, the mixing of gaseous fuel and air can be promoted.Especially
It, diesel engine 1 is set to ultra-long-stroke and combustion space is longer shape on piston reciprocating moving direction, therefore effective land productivity
With the mixing efficiently to carry out gaseous fuel of the long side direction of combustion space.And then, due to 1.0MPa is set to absolute pressure
Above and below 50MPa, more preferably it is set to the high-pressure injection gaseous fuel of more than 20MPa and below 30MPa with absolute pressure, because
This can promote the mixing of gaseous fuel further.
Therefore, it is possible to increase the Local Minimum λ (λ is excess air ratio) that local gas fuel concentration uprises, by keeping away as far as possible
Exempt from the abnormal combustions such as premature firing, detonation, it is possible to increase combustion stability.And, due to can avoid as far as possible premature firing,
The abnormal combustions such as detonation, therefore, compared with conventional premixed engine, can reduce the reduction amount of compression ratio, and can make
The reduction of the thermal efficiency minimizes it is also possible to run under the high load capacity of higher Pme (mean effective pressure in cylinder).
Pre-mixed gas valve 30 is arranged at cylinder head 11 in the same manner as air bleeding valve 12, to the direction injection away from air bleeding valve 12
Gaseous fuel, therefore, even if it is also possible to start the injection of gaseous fuel before air bleeding valve 12 completely closes.So closing
Start the injection of gaseous fuel before air bleeding valve 12, be then able to ensure that gaseous fuel is longer with the time of the mixing of air, therefore
Can more uniformly mix.
Further, it is possible to according to circumstances distinguish use pre-mixed gas fuel mode and diffusion gas fuel mode, therefore, exist
When using in ECA, select pre-mixing combustion gas mode, the NOx suppression in aerofluxuss can be transported below limits value
OK.Thus it is not necessary to be used for removing the exhaust gas treatment devices such as the SCR of NOx, for reducing the attendant equipments such as the EGR of NOx.Another
Aspect, when outside ECA, selects diffusion gas fuel mode, can carry out the higher operation of combustion stability.
And, possess the fuel oil pattern being diffused burning using fuel valve 34, fire with gas as possessing fuel oil pattern
The DF electromotor of material pattern (pre-mixed gas fuel mode and diffusion gas fuel mode) and constitute diesel engine 1, therefore, pass through
Select fuel oil pattern, the higher operation of combustion stability can be carried out.On the other hand, as long as selecting gaseous fuel pattern, then can
Enough avoid the discharge of the SOx from fuel oil, and the run time of fuel oil pattern can be reduced and suppress fuel cost.
And, due to employing premixing interim process control, therefore, switch to pre-mixed gas from diffusion gas fuel mode
It is prevented from unburned gas during fuel mode to discharge from air bleeding valve 12, described premixing interim process control is from diffusion gas fuel
Increase in the combustion stroke that pattern or diffusion fuel oil pattern have just switched in the initial circulation after pre-mixed gas fuel mode
Plus from the gaseous fuel quantity of pre-mixed gas valve 30 injection until becoming the concentration of gaseous fuel burning completely.
In addition, in above-mentioned embodiment, using pre-mixed gas valve 30 and diffusion gas valve 32 as respectively different gas
Valve is illustrated but it is also possible to these pre-mixed gas valves 30 and diffusion gas valve 32 are doubled as common gas trap.This
In the case of, it is set to following structure：Will be formed in common gas trap multiple spray orifices direction distinguish be set as premixing with
Diffusion is used, and changeable each spray orifice.
Symbol description
1- diesel engine (internal combustion engine), 9- cylinder jacket, 10- scavenging port, 11- cylinder head, 12- air bleeding valve, 13- piston, 14- arranges
Gas manifold, 16- supercharger, 30- pre-mixed gas valve (the 1st gas fuel injection valves), 32- diffusion gas valve (the 2nd gaseous fuel
Injection valve), 34- fuel valve (fuel injection valve).
Claims (according to the 19th article of modification of treaty)
1. a kind of internal combustion engine is it is characterised in that possess：
Cylinder jacket；
Piston, is moved back and forth in this cylinder jacket；
Cylinder head, is arranged at a side of described cylinder jacket；
Air bleeding valve, is arranged at this cylinder head；
Scavenging port, is arranged at the another side of described cylinder jacket；And
1st gas fuel injection valves, are arranged at described cylinder head, and into the cylinder being formed by described cylinder jacket and described cylinder head
Gas injection fuel,
Described 1st gas fuel injection valves are to this piston injection described gas combustion closed by described piston after described scavenging port
Material,
Described cylinder head is additionally provided with the 2nd gas fuel injection valves to described cylinder injection gaseous fuel,
Described internal combustion engine possesses the control unit of switching diffusion gas fuel mode and pre-mixed gas fuel mode, described diffusion gas
Fluid fuel pattern is burnt using described 2nd gas fuel injection valves, and described pre-mixed gas fuel mode utilizes the described 1st
Gas fuel injection valves are burnt.
2. internal combustion engine according to claim 1 it is characterised in that
The stroke of described piston is that Bore-to-Stroke Ratio is set to more than 3 with the ratio of the internal diameter of described cylinder jacket.
3. internal combustion engine according to claim 1 and 2 it is characterised in that
From described 1st gas fuel injection valves injection gaseous fuel pressure, with absolute pressure be set to more than 1.0MPa and
Below 50MPa.
4. internal combustion engine according to any one of claim 1 to 3 it is characterised in that
Described cylinder is covered with the fuel oil injection valve to described cylinder injection fuel oil.
5. internal combustion engine according to claim 1 it is characterised in that
Fire stroke in described control unit, in just switching to the initial circulation after described pre-mixed gas fuel mode
The middle gaseous fuel quantity increasing from the 1st gas fuel injection valves injection, until become from described 1st gas fuel injection valves spray
The concentration of the gaseous fuel penetrated burning completely.
6. internal combustion engine according to claim 1 it is characterised in that
From described 1st gas fuel injection valves gas injection fuel as pre-mixed fuel, and from described 2nd gas spray valve spray
Emanate fluid fuel as pre-mixed fuel.
7. a kind of ship it is characterised in that
Internal combustion engine any one of claim 1 to 7 is used as marine engine.
8. a kind of control method of internal combustion engine is it is characterised in that have：
1st gaseous fuel jeting process, towards this piston closed by piston after scavenging port to cylinder injection gaseous fuel；And
2nd gaseous fuel jeting process, to described cylinder injection gaseous fuel；
The diffusion gas fuel that the control method switching of described internal combustion engine is burnt by described 2nd gaseous fuel jeting process
Pattern and the pre-mixed gas fuel mode burnt by described 1st gaseous fuel jeting process.
Claims (8)
1. a kind of internal combustion engine is it is characterised in that possess：
Cylinder jacket；
Piston, is moved back and forth in this cylinder jacket；
Cylinder head, is arranged at a side of described cylinder jacket；
Air bleeding valve, is arranged at this cylinder head；
Scavenging port, is arranged at the another side of described cylinder jacket；And
1st gas fuel injection valves, are arranged at described cylinder head, and into the cylinder being formed by described cylinder jacket and described cylinder head
Gas injection fuel,
Described 1st gas fuel injection valves are to this piston injection described gas combustion closed by described piston after described scavenging port
Material.
2. internal combustion engine according to claim 1 it is characterised in that
The stroke of described piston is that bore stroke ratio is set to more than 3 with the ratio of the internal diameter of described cylinder jacket.
3. internal combustion engine according to claim 1 and 2 it is characterised in that
From described 1st gas fuel injection valves injection gaseous fuel pressure, with absolute pressure be set to more than 1.0MPa and
Below 50MPa.
4. internal combustion engine according to any one of claim 1 to 3 it is characterised in that
Described cylinder is covered with the fuel oil injection valve to described cylinder injection fuel oil.
5. internal combustion engine according to any one of claim 1 to 4 it is characterised in that
Described cylinder head is additionally provided with the 2nd gas fuel injection valves to described cylinder injection gaseous fuel,
Described internal combustion engine possesses the control unit of switching diffusion gas fuel mode and pre-mixed gas fuel mode, described diffusion gas
Fluid fuel pattern is burnt using described 2nd gas fuel injection valves, and described pre-mixed gas fuel mode utilizes the described 1st
Gas fuel injection valves are burnt.
6. internal combustion engine according to claim 5 it is characterised in that
Combustion stroke in described control unit, in just switching to the initial circulation after described pre-mixed gas fuel mode
The middle gaseous fuel quantity increasing from the 1st gas fuel injection valves injection, until become from described 1st gas fuel injection valves spray
The concentration of the gaseous fuel penetrated burning completely.
7. the internal combustion engine according to claim 5 or 6 it is characterised in that
From described 1st gas fuel injection valves gas injection fuel as pre-mixed fuel, and from described 2nd gas spray valve spray
Emanate fluid fuel as pre-mixed fuel.
8. a kind of ship it is characterised in that
Internal combustion engine any one of claim 1 to 7 is used as marine engine.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014116834A JP6746268B2 (en) | 2014-06-05 | 2014-06-05 | Internal combustion engine, ship equipped with the same, and method of controlling internal combustion engine |
| JP2014-116834 | 2014-06-05 | ||
| PCT/JP2015/066120 WO2015186768A1 (en) | 2014-06-05 | 2015-06-03 | Internal combustion engine and ship equipped with same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106460636A true CN106460636A (en) | 2017-02-22 |
| CN106460636B CN106460636B (en) | 2019-08-06 |
Family
ID=54766836
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580013177.8A Active CN106460636B (en) | 2014-06-05 | 2015-06-03 | Internal combustion engine and the ship for having the internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6746268B2 (en) |
| KR (1) | KR101918378B1 (en) |
| CN (1) | CN106460636B (en) |
| WO (1) | WO2015186768A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105910136B (en) * | 2016-04-18 | 2018-09-04 | 中国科学院工程热物理研究所 | A kind of adjustable nozzles, nozzle array and burner |
| DK179162B1 (en) * | 2016-05-02 | 2017-12-18 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | An internal combustion engine of two-stroke crosshead type, and a method of direct injection of fuel and water into a combustion chamber |
| JP7331784B2 (en) | 2020-06-01 | 2023-08-23 | Ｊｆｅエンジニアリング株式会社 | diesel engine |
| GB202213519D0 (en) * | 2022-09-15 | 2022-11-02 | Cosworth Group Holdings Ltd | Improvements in or relating to gaseous fuelled internal combustion engines |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007198275A (en) * | 2006-01-27 | 2007-08-09 | Toyota Motor Corp | Gaseous fuel internal combustion engine |
| CN101336339A (en) * | 2006-01-27 | 2008-12-31 | 丰田自动车株式会社 | Gas-fueled internal combustion engine and control method for gas-fueled internal combustion engine |
| CN101473126A (en) * | 2006-06-19 | 2009-07-01 | 丰田自动车株式会社 | Multifuel internal combustion engine |
| JP2013217334A (en) * | 2012-04-11 | 2013-10-24 | Mitsubishi Heavy Ind Ltd | 2-cycle gas engine |
Family Cites Families (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5395848A (en) | 1977-02-02 | 1978-08-22 | Sumitomo Metal Ind Ltd | Gas shielded arc welding |
| KR950019123A (en) * | 1993-12-28 | 1995-07-22 | 전성원 | Engine operation control device and method in case of overload |
| JP3300965B2 (en) * | 1994-07-05 | 2002-07-08 | 三信工業株式会社 | Two-cycle in-cylinder injection engine |
| JP3763942B2 (en) * | 1997-07-18 | 2006-04-05 | 株式会社東芝 | Gas turbine fuel supply control device |
| EP0965738A1 (en) * | 1998-06-15 | 1999-12-22 | Wärtsilä NSD Schweiz AG | Diesel engine |
| JP2000130200A (en) * | 1998-10-30 | 2000-05-09 | Mitsubishi Motors Corp | Controller for diesel engine |
| DK177917B1 (en) * | 2001-05-23 | 2015-01-05 | Man Diesel & Turbo Deutschland | Cylinder in a two-stroke long-rinsed cross-head motor and method for reducing NOx formation |
| CA2406267C (en) * | 2002-10-02 | 2013-01-08 | Westport Research Inc. | Exhaust gas recirculation methods and apparatus for reducing nox emissions from internal combustion engines |
| US8266891B2 (en) * | 2004-11-08 | 2012-09-18 | General Electric Company | Method and system for emission control of a compression ignition locomotive engine |
| JP4449817B2 (en) * | 2005-05-13 | 2010-04-14 | いすゞ自動車株式会社 | Diesel engine control device |
| JP2007177662A (en) * | 2005-12-27 | 2007-07-12 | Toyota Motor Corp | Failure determination method of fuel injection device |
| JP5371582B2 (en) * | 2009-07-02 | 2013-12-18 | 株式会社リケン | Oil scraping ring for piston rod, manufacturing method thereof, and stuffing box provided with the oil scraping ring |
| JP5589673B2 (en) * | 2010-08-20 | 2014-09-17 | マツダ株式会社 | diesel engine |
| JP5395848B2 (en) * | 2011-06-24 | 2014-01-22 | 三井造船株式会社 | Low speed 2-cycle gas engine |
| JP5949183B2 (en) | 2012-06-06 | 2016-07-06 | 株式会社Ihi | 2-stroke uniflow engine |
| JP5925104B2 (en) * | 2012-10-19 | 2016-05-25 | 三菱重工業株式会社 | Fuel gas injection valve, dual fuel gas engine, and fuel gas injection valve injection method |
-
2014
- 2014-06-05 JP JP2014116834A patent/JP6746268B2/en active Active
-
2015
- 2015-06-03 WO PCT/JP2015/066120 patent/WO2015186768A1/en active Application Filing
- 2015-06-03 CN CN201580013177.8A patent/CN106460636B/en active Active
- 2015-06-03 KR KR1020167026321A patent/KR101918378B1/en active IP Right Grant
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007198275A (en) * | 2006-01-27 | 2007-08-09 | Toyota Motor Corp | Gaseous fuel internal combustion engine |
| CN101336339A (en) * | 2006-01-27 | 2008-12-31 | 丰田自动车株式会社 | Gas-fueled internal combustion engine and control method for gas-fueled internal combustion engine |
| CN101473126A (en) * | 2006-06-19 | 2009-07-01 | 丰田自动车株式会社 | Multifuel internal combustion engine |
| JP2013217334A (en) * | 2012-04-11 | 2013-10-24 | Mitsubishi Heavy Ind Ltd | 2-cycle gas engine |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101918378B1 (en) | 2019-01-29 |
| KR20160119242A (en) | 2016-10-12 |
| JP6746268B2 (en) | 2020-08-26 |
| WO2015186768A1 (en) | 2015-12-10 |
| JP2015229973A (en) | 2015-12-21 |
| CN106460636B (en) | 2019-08-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9328693B2 (en) | Piston, engine and operating method for reduced production of particulate matter | |
| KR101677862B1 (en) | Fuel gas injection valve, dual-fuel gas engine, and fuel gas injection method | |
| KR101664640B1 (en) | 2-cycle gas engine | |
| KR101931840B1 (en) | A two-stroke internal combustion engine, method operating a two-stroke internal combustion engine and method of converting a two-stroke engine | |
| CN105940200B (en) | The compression ignition engine of fuel direct injection internal combustion engine and more specifically little compressible | |
| FI127022B (en) | Two-stroke internal combustion engine and method of operating it | |
| CN103452682B (en) | Method for operating engine | |
| JP4370586B2 (en) | Dual operation mode engine system | |
| CN106460636B (en) | Internal combustion engine and the ship for having the internal combustion engine | |
| CN104541033B (en) | Uniflow type two stroke engine | |
| KR102546911B1 (en) | Method and control device for operating an engine | |
| CN108474290A (en) | Piston head for internal combustion engine | |
| JP2021102962A (en) | Low-load operation method for operating reciprocating piston internal combustion engine, computer program product, and reciprocating piston internal combustion engine | |
| JP2018193909A (en) | Multistage injection type diesel engine, machinery provided with the same and control method of multistage injection type diesel engine | |
| US11719173B2 (en) | Method and gas fuel injection unit for operating an internal combustion engine | |
| KR101953050B1 (en) | Control device of internal-combustion engine, and ship provided with same, and method of operating internal-combustion engine | |
| JP6675887B2 (en) | Crosshead internal combustion engine | |
| KR20190045795A (en) | Engine for Ship | |
| CN114233465A (en) | Ammonia fuel combustion system, engine and combustion control method | |
| CN216518261U (en) | Ammonia fuel combustion system and engine | |
| WO2015146933A1 (en) | Piston | |
| US20040103875A1 (en) | Method and apparatus for suppressing diesel engine emissions | |
| JP2004092574A (en) | Gas engine equipped with auxiliary scavenging device | |
| NO20200463A1 (en) | Design of combustion chambers in reciprocating engines that use highly flammable fuels | |
| CN117307361A (en) | Gas ignition device of dual-fuel low-speed diesel engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20170814 Address after: Japan's Tokyo port harbor two chome 16 No. 5 Applicant after: Mit-subishi Heavy Industries Ltd. Applicant after: Japan motor Limited by Share Ltd Address before: Japan's Tokyo port harbor two chome 16 No. 5 Applicant before: Mit-subishi Heavy Industries Ltd. |
|
| TA01 | Transfer of patent application right | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |