CN100416068C - Fuel jet method - Google Patents
Fuel jet method Download PDFInfo
- Publication number
- CN100416068C CN100416068C CNB011353775A CN01135377A CN100416068C CN 100416068 C CN100416068 C CN 100416068C CN B011353775 A CNB011353775 A CN B011353775A CN 01135377 A CN01135377 A CN 01135377A CN 100416068 C CN100416068 C CN 100416068C
- Authority
- CN
- China
- Prior art keywords
- fuel
- nozzle
- work cycle
- stroke
- firing chamber
- 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.)
- Expired - Fee Related
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 60
- 238000000034 method Methods 0.000 title claims abstract description 35
- 238000002485 combustion reaction Methods 0.000 claims abstract description 20
- 238000010304 firing Methods 0.000 claims description 22
- 239000007921 spray Substances 0.000 claims description 9
- 238000002347 injection Methods 0.000 abstract description 7
- 239000007924 injection Substances 0.000 abstract description 7
- 230000002349 favourable effect Effects 0.000 description 5
- 238000005260 corrosion Methods 0.000 description 3
- 230000007797 corrosion Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 239000000779 smoke Substances 0.000 description 3
- 206010020843 Hyperthermia Diseases 0.000 description 2
- 238000007323 disproportionation reaction Methods 0.000 description 2
- 230000036031 hyperthermia Effects 0.000 description 2
- 239000002912 waste gas Substances 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 235000019504 cigarettes Nutrition 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/242—Arrangement of spark plugs or injectors
-
- 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
- F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Feeding And Controlling Fuel (AREA)
Abstract
Method for injecting fuel into a combustion chamber having at least two fuel injectors of a cylinder of a reciprocating internal combustion diesel engine in underload operation comprises alternately injecting the fuel so that during at least two successive working cycles no fuel is injected by at least one of the fuel injectors and during at least two following successive working cycles no fuel is injected by the other fuel injector. The fuel is alternately injected by a method wherein any fuel is not fed through at least one nozzle during a series of duty cycle of at least two times and thereafter, any fuel is not fed by another injection nozzle.
Description
Technical field
The present invention relates to when sub load turns round fuel sprayed into the method in the reciprocating piston type cylinder of diesel engine internal furnace.
Background technique
According to EP 0 775 821 specifications, knownly a kind of fuel is sprayed into method in the firing chamber in the low speed reciprocating piston type cylinder of diesel engine.Fuel utilizes two to four fuel nozzles to spray in the firing chamber, and these nozzles are worked in whole load range continuously.Especially between the sub load on-stream period, the fuel quantity of a power stroke defined is only by a nozzle ejection, and in next power stroke, the fuel quantity of defined is through second nozzle ejection, therefore, in each power stroke, required fuel quantity is alternately sprayed by each nozzle.
The shortcoming of this injection method is especially to produce partial combustion when sub load turns round in the firing chamber, and therefore the waste gas of burning has a large amount of visible smokes.
Summary of the invention
The objective of the invention is the reciprocating piston type diesel engine that to turn round by this way, make it have operating condition preferably.
This purpose realizes by means of following method: when sub load turns round, fuel is sprayed in the firing chamber of reciprocating piston type cylinder of diesel engine, each firing chamber is being provided with at least two nozzles, its characteristics are that fuel is alternately sprayed by this way, make at least two continuous work cycle at least one nozzle in need not this at least two nozzle come burner oil, and subsequently at least two continuous work cycle, another nozzle in need not this at least two nozzle comes burner oil.
Other favorable method step is: two, three or four nozzles are provided for each firing chamber, by described nozzle ejection fuel; In at least two continuous cycles by same nozzle ejection fuel, then at least two continuous cycles by another nozzle ejection fuel; In all cases, by a burner oil in these nozzles, and at least two continuous work cycle same nozzle ejection fuel, then at least two continuous work cycle by another nozzle ejection fuel; In the time lag at least 3 seconds, by same nozzle burner oil continuously, at 5 to 60 seconds, especially in the time lag between 10 to 30 seconds, by same nozzle ejection fuel, stroke piston combustion engine is to turn round less than 10% full-power sub load, and stroke piston combustion engine is as four-stroke or two stroke diesel engine work, when sub load turns round, at least two continuous work cycle by one or two or three nozzle ejection fuel.
This purpose especially realizes by means of a kind of method that is suitable for when sub load turns round fuel sprayed in the reciprocating piston type cylinder of diesel engine internal furnace, wherein each firing chamber and at least two nozzles link, fuel alternately sprays in this manner, make at least two continuous work cycle without in this two nozzle at least one fuel is sprayed into, then at least two continuous work cycle, fuel is sprayed into without another nozzle.
This method allows to produce a high-temperature zone in the firing chamber.In a kind of method for optimizing, at least 3 seconds, be preferably in time lag of 10 to 30 seconds, claim all that ground sprays with same nozzle with fuel is non-, so that when long-time running, in this zone of combustion, produce high temperature.The advantage that can see this method is disclosed comparing in the specification with EP 0 775 821, and the number of times that heat load changes has reduced, and this fatigue to material has favorable influence.In this zone of combustion and on every side, localized hyperthermia reduces visible smoke.Only the advantage with a nozzle ejection fuel is that fuel is longer through the discharge time of this nozzle, produces a stable injection with repeatability thus.It is disadvantageous in the continuous variation between each nozzle between injection period heat load being changed.
For example from the specification of EP 0 775 821, the expert knows that generally temperature distributing disproportionation is imperfect in the firing chamber, because for example, can produce high temperature corrosion in the hot-zone.In addition, the expert is known, and this uneven temperature distribution can cause big stress on cylinder and piston, and it is tired that this has also aggravated material.Therefore, the expert tries hard to avoid as far as possible the uneven temperature in the firing chamber to distribute according to its professional knowledge.
Yet, be surprised to find, when sub load turns round, especially only open a nozzle and can produce following advantage:
Burning occurs in same place, and therefore, in this zone of combustion, formation has the local hot spots of high temperature.This burns fuel more completely, thereby reduces the visible smoke in the gas of combustion.
Although temperature distributing disproportionation is even, yet do not produce dangerous high temperature corrosion on piston, because when sub load, on the whole, temperature value is lower;
Compare with the situation that changes nozzle in each work cycle, prolonged such as the operating life of the combustion chamber components of piston, cylinder head and outlet valve, because by means of injection method of the present invention, the number of times that heat load changes has reduced, and this has just alleviated fatigue of materials.
In all cases, fuel is preferably through a nozzle ejection.The sub load running causes the bulk temperature value lower.Therefore, the heavily stressed of combustion chamber components that is caused by uneven temperature distribution is restricted, and like this, do not produce too high or dangerous stress on combustion chamber components.Because the bulk temperature value is lower, also got rid of because of firing chamber localized hyperthermia and caused high temperature corrosion.
Method of the present invention is particularly suitable for being lower than 15% full-power utmost point lower part load running, is particularly suited for the sub load running between 1%～3% full load.
Method of the present invention allows burning free from environmental pollution when sub load turns round, and has the obvious advantage of the waste gas smoke, mists and clouds of the grey of having avoided disturbing vision or black.This is particularly advantageous for marine diesel engine.
Method of the present invention is applicable to the running of fixed and portable two-stroke and four-cycle diesel, is particularly useful for cylinder diameter greater than 150mm or greater than the four-cycle diesel of 300mm.
For example, a firing chamber and three or four nozzles link.This diesel engine can turn round by following running operating mode according to load:
When full load operation, fuel is supplied with the firing chamber through all three or four nozzles;
In first portion's load range between 25～15% full load, fuel sprays into the firing chamber through two nozzles;
In less than 15% full-power second portion load range fuel only a nozzle in three or four nozzles spray into the firing chamber.
During in switching to cited three running operating modes one, the switching of nozzle is gone into and is switched that the switching function that utilization has hysteresis be favourable.Like this, for example, between the first and second sub load scopes, switch and to be undertaken by this sample loading mode, begin with first portion's load range, switch to running operating mode with 12.5% full-power sub load by the second portion load range, and, switch to running operating mode by first portion's load range with 17.5% full-power sub load from the second portion load range.
Switch to another running operating mode from a running operating mode, for example, also can utilize the time to control this mode and carry out, make after certain moment, for example drop to be lower than or surpass a predetermined threshold value after 20 seconds, forward another changing of operating mode of turning round to and cut.Also can carry out to the switching of another running operating mode from a running operating mode, like this, the switching that forwards another running operating mode to can be carried out immediately greater than for example 5% load variations with suddenling change.
With reference to each accompanying drawing, below by exemplary embodiment explanation the present invention.
Description of drawings
Fig. 1 is a two stroke diesel engine sketch;
Fig. 2 a is the planimetric map with firing chamber of one-stroke nozzle;
Fig. 2 b is the planimetric map with firing chamber of two-stroke nozzle.
Embodiment
Hereinafter, work cycle is understood to mean the process that is taken place between the stroke piston combustion engine on-stream period, start comprising valve, combustion jet, the discharge of burning and combustion gas is in the two-stroke machine, work cycle is finished between a commentaries on classics usually, and finishes after two change in the four-stroke machine.
Fig. 1 represents a two stroke diesel engine 1, and some cylinders 11 and piston 10 are arranged, and wherein, cooperatively interacting between the motion of bent axle 2, burning conveying and outlet valve 13 is electronically controlled.Utilize a high-pressure service pump 4 by the road 6 and accumulator 5 fuel is defeated by nozzle 12.The location that comprises the hydraulic system permission start outlet valve 13 of pressure pump 7, pipeline 9 and accumulator 8.The outlet valve 13 of this longitudinally scavenged two stroke diesel engine 1 center arrangement and plurality of nozzles 12, they are along the cylinder head arranged around.Usually, this two stroke diesel engine has two to four fuel nozzles 12.
Fig. 2 a simply represents the firing chamber of cylinder 11, has three nozzle 12a, 12b, 12c, they with the gap that equates along circumference.The running of the case representation sub load of this method in all cases, has a main jet 12a, and shown in constantly, no fuel 14 is through nozzle 12b and 12c injection.In at least two continuous work cycle, fuel 14a is only sprayed by nozzle 12a, and then at least two continuous work cycle, fuel 14a is only sprayed by nozzle 12b, then in two continuous work cycle at least again, is only sprayed by nozzle 12c.In a kind of particularly advantageous method, in two continuous operation cycle periods basically, for example during 10 to 30 seconds, fuel is supplied with by a nozzle 12a.After this at one time in the cycle, fuel is only supplied with by nozzle 12b, is only supplied with by nozzle 12c then.This method makes combustion chamber temperature even, thereby forms the zone of combustion with high temperature, and the result makes burning that cigarette seldom be arranged.Fuel at first nozzle 12a sprays, and is then sprayed by nozzle 12c by nozzle 12b then.The order of nozzle also can change, and makes them with nozzle 12c, the order work of nozzle 12b and nozzle 12a.
Fig. 2 b is illustrated in a method example in the sub load running, in all cases, two nozzle 12a is arranged, and 12b works at the same time.Be similar to the exemplary embodiment of Fig. 2 a, fuel 14a, 14b are equally only supplied with by nozzle 12a, 12b at least two continuous work cycle, are supplied with by nozzle 12c, 12a then.This method is continued to repeat.1 arrives another to before nozzle 12b, the 12c shown in Fig. 2 a, in 5 to 60 seconds, in 10 to 30 seconds, is particularly advantageous by two same nozzle 12a, 12b burner oil 14a, 14b especially.
Only be illustrated at this two methods example shown in Fig. 2 a and the 2b how fuel 14a, 14b can be by two examples in non-a large amount of possibilities of spraying with all claiming in a two-stroke or the four-cycle diesel, in all cases, 11 2 to four fuel nozzles 12 of every cylinder are only opened the part in the existing nozzle, to reach long and more stable injection duration, and make combustion chamber temperature reach temporary transient uneven distribution, promptly between the sub load on-stream period, obtain a high temperature combustion zone.
When 1% to 15% full-power utmost point lower part is loaded, press the method shown in Fig. 2 a, in all cases, be particularly advantageous with main jet 12a, 12b, a 12c.The size of these nozzles 12a, 12b, 12c is applicable to rated load and turns round.In order to reach favourable spray regime, under low sub load, it is favourable by nozzle 12a, a 12b, 12c less fuel quantity being supplied with the firing chamber.
Claims (9)
- One kind when sub load turns round with fuel (14a, 14b) spray into method in the firing chamber of reciprocating piston type diesel engine (1) cylinder (11), each firing chamber is being provided with at least two nozzle (12a, 12b, 12c), it is characterized in that fuel (14a, 14b) alternately sprayed by this way, making at least two continuous work cycle need not this at least two nozzle (12a, 12b, at least one nozzle 12c) comes burner oil, and subsequently at least two continuous work cycle, need not this at least two nozzle (12a, 12b, another nozzle 12c) come burner oil (14a, 14b).
- 2. the method for claim 1 is characterized in that providing two, three or four nozzles to each firing chamber, by described nozzle ejection fuel.
- 3. method as claimed in claim 1 or 2 is characterized in that at least two continuous cycles by same nozzle ejection fuel; Then at least two continuous cycles by another nozzle ejection fuel.
- 4. the method for claim 1 is characterized in that in all cases, by a burner oil in these nozzles; And at least two continuous work cycle by same nozzle ejection fuel; Then at least two continuous work cycle by another nozzle ejection fuel.
- 5. the method for claim 1 is characterized in that at least 3 seconds the time lag, by same nozzle burner oil continuously.
- 6. method as claimed in claim 4 is characterized in that at 5 to 60 seconds, perhaps in the time lag between 10 to 30 seconds, by same nozzle ejection fuel.
- 7. the method for claim 1 is characterized in that stroke piston combustion engine is to turn round less than 10% full-power sub load.
- 8. the method for claim 1 is characterized in that stroke piston combustion engine is as four-stroke or two stroke diesel engine work.
- 9. the method for claim 1 is characterized in that when partial load is turned round, and comes burner oil by independent one or two nozzles at least two continuous work cycle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP00810932 | 2000-10-10 | ||
| EP00810932.4 | 2000-10-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1346934A CN1346934A (en) | 2002-05-01 |
| CN100416068C true CN100416068C (en) | 2008-09-03 |
Family
ID=8174961
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB011353775A Expired - Fee Related CN100416068C (en) | 2000-10-10 | 2001-10-09 | Fuel jet method |
Country Status (9)
| Country | Link |
|---|---|
| EP (1) | EP1197650B1 (en) |
| JP (1) | JP5009467B2 (en) |
| KR (1) | KR100743210B1 (en) |
| CN (1) | CN100416068C (en) |
| AT (1) | ATE298393T1 (en) |
| DE (1) | DE50106574D1 (en) |
| DK (1) | DK1197650T3 (en) |
| PL (1) | PL199837B1 (en) |
| TW (1) | TW491930B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5693189B2 (en) * | 2010-12-08 | 2015-04-01 | 三菱重工業株式会社 | Fuel injection apparatus for internal combustion engine and fuel injection method for internal combustion engine |
| JP5984469B2 (en) * | 2012-04-11 | 2016-09-06 | 三菱重工業株式会社 | Dual fuel diesel engine |
| JP5998671B2 (en) * | 2012-06-27 | 2016-09-28 | 株式会社Ihi | 2-cycle engine |
| DE102017201586A1 (en) | 2017-02-01 | 2018-08-02 | Robert Bosch Gmbh | Internal combustion engine with redundant injectors |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0775821A1 (en) * | 1995-11-24 | 1997-05-28 | New Sulzer Diesel Ag | Method and apparatus for injecting fuel in a reciprocating internal combustion engine |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR840465A (en) * | 1937-08-06 | 1939-04-26 | Porsche Kg | Fast running internal combustion engine, in particular for motor vehicles and airplanes |
| US2640422A (en) * | 1946-12-03 | 1953-06-02 | Texas Co | Fuel pump for internal-combustion engines |
| CH665453A5 (en) * | 1985-01-11 | 1988-05-13 | Sulzer Ag | CYLINDER COVER FOR A PISTON INTERNAL COMBUSTION ENGINE. |
| JPS62118055A (en) * | 1985-11-16 | 1987-05-29 | Mitsubishi Heavy Ind Ltd | Variable injection nozzle fuel injection valve |
| JPH06173821A (en) * | 1992-12-09 | 1994-06-21 | Mazda Motor Corp | Fuel injection device for engine |
-
2001
- 2001-08-20 TW TW090120416A patent/TW491930B/en not_active IP Right Cessation
- 2001-09-11 DK DK01810878T patent/DK1197650T3/en active
- 2001-09-11 DE DE50106574T patent/DE50106574D1/en not_active Expired - Lifetime
- 2001-09-11 EP EP01810878A patent/EP1197650B1/en not_active Expired - Lifetime
- 2001-09-11 AT AT01810878T patent/ATE298393T1/en not_active IP Right Cessation
- 2001-09-17 KR KR1020010057320A patent/KR100743210B1/en active IP Right Grant
- 2001-09-28 JP JP2001299881A patent/JP5009467B2/en not_active Expired - Fee Related
- 2001-10-05 PL PL349991A patent/PL199837B1/en not_active IP Right Cessation
- 2001-10-09 CN CNB011353775A patent/CN100416068C/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0775821A1 (en) * | 1995-11-24 | 1997-05-28 | New Sulzer Diesel Ag | Method and apparatus for injecting fuel in a reciprocating internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| DE50106574D1 (en) | 2005-07-28 |
| DK1197650T3 (en) | 2005-07-11 |
| KR100743210B1 (en) | 2007-07-26 |
| EP1197650B1 (en) | 2005-06-22 |
| JP2002155782A (en) | 2002-05-31 |
| JP5009467B2 (en) | 2012-08-22 |
| TW491930B (en) | 2002-06-21 |
| ATE298393T1 (en) | 2005-07-15 |
| PL199837B1 (en) | 2008-11-28 |
| CN1346934A (en) | 2002-05-01 |
| EP1197650A1 (en) | 2002-04-17 |
| KR20020028778A (en) | 2002-04-17 |
| PL349991A1 (en) | 2002-04-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100516475C (en) | Strategy for fueling a diesel engine | |
| CN101427019B (en) | Low emission high performance engines, multiple cylinder engines and operating methods | |
| US7270108B2 (en) | Opposed piston, homogeneous charge pilot ignition engine | |
| CN1934340B (en) | Method for operating compressed ignition engine and the compressed ignition engine | |
| EP0890725A3 (en) | Apparatus for and method of controlling internal combustion engine | |
| US6595182B2 (en) | Direct fuel injection and ignition system for internal combustion engines | |
| CN103511104A (en) | An internal combustion engine with control of fuel gas injection pressure | |
| CN103925119A (en) | Gaseous common rail fuel system and high compression ratio engine using same | |
| CN102884298A (en) | Fuel injection rate shaping in an internal combustion engine | |
| CN104471203A (en) | Internal combustion engine with a first and a second injector | |
| CN108730053A (en) | The control device of internal combustion engine | |
| US20160160742A1 (en) | Engine system having enriched pre-chamber spark plug | |
| CN101484680A (en) | Fuel injection control method for a direct injection spark ignition internal combustion engine | |
| CN102918240B (en) | For the method and apparatus supplying fuel in internal combustion engine | |
| CN100416068C (en) | Fuel jet method | |
| CN102022209B (en) | Injection method and device for controlling an injection process in an internal combustion engine | |
| US8069835B2 (en) | Internal combustion engine and operating method therefor | |
| GB2530761A (en) | Fuel injection equipment | |
| CN108930621A (en) | Large-sized diesel motor and method for operating large-sized diesel motor | |
| CN106133298B (en) | Inject fuel into the method in internal combustion engine | |
| SE9901255L (en) | Procedure for fuel injection in an internal combustion engine and internal combustion engine | |
| CN1788147A (en) | In-cylinder combustion recipe for meeting tier 2 locomotive emissions regulations | |
| CN110374740A (en) | For operating the method and control device of dual fuel engine | |
| CN103670769A (en) | Injector configuration of a cylinder head of a dual fuel internal combustion engine | |
| RU2644795C1 (en) | Internal combustion 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 | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080903 Termination date: 20201009 |