CN106285970B - A kind of dual fuel engine control method of cold start - Google Patents
A kind of dual fuel engine control method of cold start Download PDFInfo
- Publication number
- CN106285970B CN106285970B CN201510282518.3A CN201510282518A CN106285970B CN 106285970 B CN106285970 B CN 106285970B CN 201510282518 A CN201510282518 A CN 201510282518A CN 106285970 B CN106285970 B CN 106285970B
- Authority
- CN
- China
- Prior art keywords
- cold start
- dual fuel
- fuel engine
- revolving speed
- diesel oil
- 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.)
- Active
Links
Landscapes
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
The present invention provides a kind of dual fuel engine control method of cold start, are related to technical field of engines, to solve the problems, such as that several circulations are easy to catch fire before cold start；It according to current coolant temperature, obtains cold start revolving speed first；Then according to cold start revolving speed, cold start dual fuel engine, until automobile is in idle state.The present invention determines that cold start revolving speed, the cold start revolving speed that this method of determination obtains are higher than cold start rotary speed of diesel engine using coolant temperature；When the cold start revolving speed to determine in this way, when cold start dual fuel engine, the crankshaft of dual fuel engine and the inertia of rotation system can be increased, to improve diesel oil cylinder temperature rapidly, it avoids catching fire, to make automobile complete cold start and in idle running, to reduce the total hydrocarbon emissions amount of dual fuel engine, which is applied in dual fuel engine cold-start period.
Description
Technical field
The present invention relates to technical field of engines, in particular to a kind of dual fuel engine control method of cold start.
Background technique
Common engine is gasoline-fueled petrol engine, or using diesel oil as the diesel engine of fuel, but
It is that this engine consumption is big and the discharge amount of nitrogen oxides and soot is high；For this purpose, a kind of dual fuel engine is had devised,
It is to drive automobile runs using gasoline and diesel oil as fuel combination, wherein gasoline enters diesel oil cylinder by air intake duct, and diesel oil is logical
It crosses the nozzle on diesel oil cylinder to spray into diesel oil cylinder, mixes diesel oil with gasoline, compression ignition is to carry out piston acting.Compared to traditional
Diesel engine, although dual fuel engine oil consumption is small, the discharge amount of nitrogen oxides and soot is low, the discharge amount of its total hydrocarbon compared to
Conventional diesel engine is but higher by ten times or so.
By to dual fuel engine the study found that the total hydrocarbon of dual fuel engine occurs mainly with cold-start period
In, the reason is that: the optimal compression ratio (generally 14 or so) of dual fuel engine is lower than the compression ratio of diesel engine, and compression is eventually
The mixture temperature and pressure of point are lower, so that dual fuel engine is not easy cold start, it is highly unstable in preceding several circulations,
Dual fuel engine is easy to catch fire, so that increasing the discharge amount of total hydrocarbon.
Summary of the invention
In view of this, the present invention is directed to propose a kind of dual fuel engine control method of cold start, double to solve cold start
Several circulations are easy the problem of catching fire before engine fuel.
In order to achieve the above objectives, the technical scheme of the present invention is realized as follows:
A kind of dual fuel engine control method of cold start, comprising the following steps:
Step S1: it according to coolant temperature current in dual fuel engine, obtains under current coolant temperature corresponding
Cold start revolving speed；The corresponding cold start revolving speed, is higher than current coolant temperature cold start bavin under current coolant temperature
Revolving speed corresponding to oil turbine；
Step S2: the cold start revolving speed corresponding under the current coolant temperature, cold start dual fuel engine,
Until automobile is in idle state.
Preferably, in the step S1, corresponding cold start revolving speed is 1500rpm- under the current coolant temperature
2500rpm。
Preferably, the step S1 further include: according to the current coolant temperature, obtain and maintain the current coolant liquid
At a temperature of the time required to corresponding cold start revolving speed, when executing the step S2, according to maintaining the current coolant temperature
The time required to lower corresponding cold start revolving speed, cold start dual fuel engine.
Preferably, maintaining cold start revolving speed required time corresponding under the current coolant temperature is 10s-30s.
Preferably, in the step S2, before cold start dual fuel engine, determine that diesel oil starts spray with the following method
Then oil mass starts distributive value according to the determining diesel oil, cold start dual fuel engine:
According to cold start revolving speed corresponding under the current coolant temperature, obtain maintaining the current coolant temperature
The friction torque of lower corresponding cold start revolving speed；According to rubbing for cold start revolving speed corresponding under the current coolant temperature
Torque is wiped, diesel oil starts distributive value when determining the cold start dual fuel engine.
Preferably, in the step S2, when cold start dual fuel engine, started needed for nozzle injection the process of diesel oil according to
It is secondary by spraying in advance, main jet and after spray three phases；Wherein, the rear number sprayed is 2-4 times.
Further, the rear number sprayed selects in accordance with the following methods in the step S2:
Under Current Temperatures, if the ratio that diesel oil starts distributive value and presently described rear spray number i in spray after described is greater than
Minimum diesel oil starting distributive value is sprayed after being equal to, it is presently described rear spray number i that number is sprayed after described；Otherwise, the rear spray number
For i-1.
Further, in the step S2, before cold start dual fuel engine, diesel oil starts distributive value in the pre- spray
Starting distributive value with diesel oil in the main jet is according under the current coolant temperature and the current coolant temperature
What corresponding cold start revolving speed determined, when executing the step S2, distributive value and the main jet are started according to diesel oil in pre- spray
Middle diesel oil starts distributive value, cold start dual fuel engine.
Further, when the cold start dual fuel engine, diesel oil starts distributive value and is greater than diesel oil in the pre- spray
Diesel oil starts the sum of distributive value in dynamic distributive value and the main jet.
Preferably, in the step S2, when the automobile is in idle state, the revolving speed of the dual fuel engine
For 600rpm-800rpm.
Compared with the existing technology, dual fuel engine control method of cold start of the present invention has the advantage that
Dual fuel engine control method of cold start provided by the invention has determined current coolant liquid using coolant temperature
At a temperature of corresponding cold start revolving speed, and cold start revolving speed corresponding under current coolant temperature is higher than current coolant liquid temperature
Spend revolving speed corresponding to cold start diesel engine；When cold start corresponding under the current coolant temperature to determine in this way
Revolving speed when cold start dual fuel engine, can increase the crankshaft of dual fuel engine and the inertia of rotation system, to mention rapidly
High diesel oil cylinder temperature, avoids catching fire, so that automobile be made to complete cold start and in idle running, at this point, by cold start
The revolving speed of dual fuel engine is in rated speed when auto idle speed operating condition, to reduce the total hydrocarbon of dual fuel engine
Discharge amount.
Detailed description of the invention
The attached drawing for constituting a part of the invention is used to provide further understanding of the present invention, schematic reality of the invention
It applies example and its explanation is used to explain the present invention, do not constitute improper limitations of the present invention.In the accompanying drawings:
Fig. 1 is dual fuel engine control method of cold start flow chart described in the embodiment of the present invention；
Fig. 2 is dual fuel engine control method of cold start schematic diagram described in the embodiment of the present invention；
Fig. 3 is that rear spray number determines schematic diagram in dual fuel engine described in the embodiment of the present invention；
Fig. 4 is bavin in diesel oil distributive value and rear spray in diesel oil distributive value in pre- spray, main jet described in the embodiment of the present invention
The determination schematic diagram of oily distributive value；
Fig. 5 is dual fuel engine control method of cold start flow chart described in optimum embodiment of the present invention.
Description of symbols:
1, diesel oil starts distributive value, and 2, diesel oil starts distributive value in pre- spray, 3, diesel oil starts distributive value, 4, rear spray in main jet
Middle diesel oil starts distributive value, 5, it is rear spray minimum diesel oil and start distributive value, 6, be able to reflect different coolant temperatures and engine is cold
The curve of starting speed, 7, be able to reflect the corresponding curve maintained the time required to cold start revolving speed of different coolant temperatures, 8,
Engine torque MAP, 9, the total oil mass MAP10 of engine, pre- distributive value MAP, 11, main jet oil mass MAP.
Specific embodiment
It should be noted that in the absence of conflict, the feature in embodiment and embodiment in the present invention can phase
Mutually combination.
The present invention will be described in detail below with reference to the accompanying drawings and embodiments.
Referring to Fig. 1, the embodiment of the invention provides a kind of dual fuel engine control method of cold start, including following step
It is rapid:
Step S1:
According to coolant temperature current in dual fuel engine, obtains cold start corresponding under current coolant temperature and turn
Speed；Wherein, cold start revolving speed corresponding under current coolant temperature is higher than current coolant temperature cold start diesel engine
Corresponding revolving speed；
Step S2: the cold start revolving speed corresponding under current coolant temperature, cold start dual fuel engine, until
Automobile is in idle state；
Step S1 has determined cold start corresponding under current coolant temperature using coolant temperature in above-described embodiment
Revolving speed, and cold start revolving speed corresponding under the obtained current coolant temperature of this method of determination is higher than current coolant temperature
Cold start revolving speed corresponding to lower diesel engine；When cold start corresponding under the current coolant temperature to determine in this way
Revolving speed when cold start dual fuel engine, can increase the crankshaft of dual fuel engine and the inertia of rotation system, to mention rapidly
High diesel oil internal cylinder temperature, avoids catching fire, so that automobile be made to complete cold start and in idle running, at this point, by cold start
Rated speed when being in auto idle speed operating condition of the revolving speed of dual fuel engine, to reduce the total of dual fuel engine
Hydrocarbon discharge amount.
It should be noted that cold start revolving speed corresponding under current coolant temperature is according to cold in dual fuel engine
But liquid temperature is found by being able to reflect the curve 6 of different coolant temperatures and engine cold starting revolving speed.In addition, embodiment
In the coolant liquid that is related to be common automobile cooling, therefore do not elaborate.
Moreover, the curve 6 for being able to reflect different coolant temperatures and engine cold starting revolving speed can be existing automobile
The corresponding curve of engine is also possible to specifically be searched by table one given below, if not providing in table one needs
The temperature to be searched can be obtained with difference approach；In addition, the corresponding cold start of the coolant temperature not provided in table one turns
Speed, can not represent can not be searched using the table one provided.
The different coolant temperatures of table one and engine cold starting revolution counter
The inertia of the crankshaft of dual fuel engine and rotation system in order to further increase improves rapidly temperature in diesel oil cylinder
Degree, avoids catching fire, and cold start revolving speed corresponding under current coolant temperature is 1500rpm-2500rpm in step S1, preferably
, cold start revolving speed corresponding under current coolant temperature is 1500rpm, 2000rpm or 2500rpm in step S1.
Referring to Fig. 4, step S1 is being obtained in dual fuel engine control method of cold start provided by the above embodiment
Under current coolant temperature after corresponding cold start revolving speed, it can also obtain according to current coolant temperature and remain current cold
But the time required to cold start revolving speed corresponding at a temperature of liquid, then step S2 is being executed) when, it not only needs according to current cooling
Corresponding cold start revolving speed at a temperature of liquid, cold start dual fuel engine, but also need according to the current coolant liquid temperature of maintenance
The time required to the lower corresponding cold start revolving speed of degree, cold start dual fuel engine.
The reason of the time required to determining cold start revolving speed corresponding under current coolant temperature in this way, is: only working as
Corresponding cold start revolving speed is kept for the sufficiently long time under preceding coolant temperature, and the temperature of diesel oil cylinder can just be increased to and is enough
It avoids catching fire, automobile is made to be finally completed cold start and is in idle state.
Preferably, maintaining cold start revolving speed required time corresponding under current coolant temperature is 10s-30s, specifically
, maintaining cold start revolving speed required time corresponding under current coolant temperature is 10s, 20s, 25s or 30s, but is not limited to
This, is enough to be avoided to catch fire as long as the temperature of diesel oil cylinder can be made to be increased to, and so that automobile is finally completed cold start and is in idling fortune
Turn state.
It is that basis is worked as it should be noted that maintaining cold start revolving speed required time corresponding under current coolant temperature
The temperature of preceding coolant liquid, by being able to reflect the corresponding curve 7 maintained the time required to cold start revolving speed of different coolant temperatures
It obtains.
In addition, the curve 7 the time required to being able to reflect that different coolant temperatures are corresponding and maintaining cold start revolving speed can be
Existing automobile engine homologous thread also can use table two given below and specifically search, if do not provided in table two
The temperature required to look up can be obtained with difference approach.And corresponding cold of the maintenance of coolant temperature not provided in table two
The time required to turn speed, can not represent can not be searched using the table two provided.
Table the time required to the corresponding maintenance cold start revolving speed of the different coolant temperatures of table two
In the step S2 of dual fuel engine control method of cold start provided by the above embodiment, cold start double fuel starts
It before machine, can also first determine that diesel oil starts distributive value 1, distributive value 1, cold start double fuel hair are then started according to determining diesel oil
Motivation；Determine that method is as follows:
It obtains maintaining current cooling according to cold start revolving speed corresponding under current coolant temperature please continue to refer to Fig. 4
The friction torque of corresponding cold start revolving speed at a temperature of liquid；According to cold start revolving speed corresponding under current coolant temperature
Friction torque, diesel oil starts distributive value 1 when determining cold start dual fuel engine.
After having determined that diesel oil starts distributive value 1, not only to be turned according to cold start corresponding under current coolant temperature
Speed, it is also necessary to start distributive value 1, cold start dual fuel engine according to the complete diesel oil of determination.
During cold start dual fuel engine can accurately be controlled in this way, diesel oil required for dual fuel engine is started
Distributive value either from the point of view of diesel oil utilization rate, or from the consideration of the success rate of cold start dual fuel engine, rises
Optimization function is arrived.
It is basis it should be noted that maintaining the friction torque of cold start revolving speed corresponding under current coolant temperature
Corresponding cold start revolving speed, is obtained by engine torque MAP8 under current coolant temperature；Cold start double fuel starts
Diesel oil starts distributive value 1 when machine, is to be obtained according to current coolant temperature by the total oil mass MAP9 of engine.
Wherein, engine torque MAP8 not only can be existing automobile engine torque MAP, can also be given using following
Table three out is searched, and the corresponding friction torque of the coolant temperature not reflected in table three can be obtained using differential technique
It arrives.Moreover, corresponding to friction torque under the different coolant temperatures and cold start revolving speed that do not provide in table three, can not represent
It can not be searched using the table three provided.
Friction torque table is corresponded under the different coolant temperatures of table three and cold start revolving speed
In addition, the total hydrocarbon emissions amount due to dual fuel engine is higher, in actual work, usually cooperation handles total hydrocarbon
Oxidation catalyst work, but since in dual fuel engine cold-start period, oxidation catalyst is in environment
Temperature, operating temperature is 170 DEG C, total to reduce therefore, it is necessary to make oxidation catalyst be preheated to operating temperature as early as possible
Hydrocarbon discharge amount.
For this purpose, in the step S2 of dual fuel engine control method of cold start provided by the above embodiment, it is also necessary to spray
The process that diesel oil is started needed for mouth injection optimizes, method particularly includes:
Fig. 2-3 is please referred to, in cold start dual fuel engine, the process that diesel oil is started needed for nozzle injection is successively passed through
Pre- spray, main jet and after spray three phases；Wherein, spray number i is 2-4 times afterwards.
In cold start dual fuel engine, dual fuel engine is in institute under the current coolant liquid that above-described embodiment determines
Under corresponding cold start revolving speed, by spraying number i after increasing, so that delivery temperature is increased sharply, oxidation catalyst is carried out pre-
Heat makes to be increased to operating temperature in the temperature short time of oxidation catalyst；Moreover, can also be burnt by repeatedly rear spray cold
In starting process, by spray in advance with main jet burn caused by soot and total hydrocarbon, further reduced the discharge of total hydrocarbon and soot
Amount.
In addition, when high with coolant temperature relative ambient temperature, in order to remain corresponding under current coolant temperature
Cold start revolving speed, the friction torque for needing to overcome also are being gradually reduced, and diesel oil starts distributive value and also gradually decreasing accordingly, institute
With the rear number i that sprays can also make corresponding adjustment.
In order to which diesel oil starts distributive value and is adapted at a temperature of spray number after making and current coolant liquid, it is rear spray number according to
Lower method is selected:
Under Current Temperatures, if diesel oil starts distributive value 4 in rear spray and the ratio of presently described rear spray number i is more than or equal to
Minimum diesel oil starting distributive value 5 is sprayed afterwards, and the rear number that sprays is presently described rear spray number i；Otherwise, spray number is i-1 afterwards.
Such as: if when cold start, coolant temperature is -20 DEG C, corresponding cold start turns under current coolant temperature
Speed is 1950rpm, maintains this revolving speed 38s, finds starting torque by engine torque MAP8 at this time and correspond to 150Nm, at this time
It is scaled come cold start dual fuel engine when, diesel oil start distributive value 1 be every circulation 30mg, according to engine speed and torque
The oil mass of pre- spray, main jet is found, 30mg subtracts diesel oil in pre- spray and starts diesel oil starting distributive value 3 in distributive value 2 and the main jet,
Minimum diesel oil is sprayed after being greater than divided by 4 corresponding oil masses and starts distributive value 5, then is sprayed after carrying out four times.
If coolant temperature rises, then the starting obtained according to revolving speed and the looked into map of temperature in cold-start period
Torque reduces, and total oil mass of corresponding starting at this time reduces naturally, and with diesel oil starts oil spout in spray after using again at this time
Amount 4 starts distributive value 5 if it is less than the minimum diesel oil of rear spray, then diesel oil starts distributive value in spray after decreasing up to rear spray number
Until 4 start distributive value 5 if it is larger than or equal to the minimum diesel oil of rear spray.
Started needed for being sprayed due to nozzle the process of diesel oil successively by spraying in advance, main jet and after spray three phases, and it is above-mentioned
When cold start dual fuel engine in embodiment, diesel oil start distributive value 1 include in pre- spray diesel oil start distributive value 2, main jet
Middle diesel oil starts diesel oil in distributive value 3 and rear spray and starts distributive value 4；So diesel oil starts distributive value 1 and is naturally larger than in pre- spray
Diesel oil starts diesel oil in distributive value 2 and main jet and starts the sum of distributive value 3.
Referring to Fig. 4, diesel oil starts diesel oil in distributive value 2 and main jet and starts distributive value 3 in pre- spray in above-mentioned steps S2
It is according to current coolant temperature, and cold start revolving speed corresponding under current coolant temperature determines.Wherein, in pre- spray
It is according to current coolant temperature that diesel oil, which starts distributive value 2, and cold start revolving speed corresponding under current coolant temperature is logical
It crosses pre- distributive value MAP10 to determine, it is according to current coolant temperature and current coolant liquid that diesel oil, which starts distributive value 3, in main jet
At a temperature of corresponding cold start revolving speed pass through main jet oil mass MAP11 determination.
The dual fuel engine control method of cold start provided in order to better illustrate the present invention, provides below with reference to Fig. 5
One optimum embodiment.
Step S1: according to current coolant temperature, cold start revolving speed corresponding under current coolant temperature is obtained；Its
In, corresponding cold start revolving speed is 1500rpm-2500rpm under current coolant temperature；It is corresponding under current coolant temperature
Cold start revolving speed be higher than current coolant temperature cold start diesel engine corresponding to revolving speed；
Step S2: according to current coolant temperature, the cold start revolving speed for remaining corresponding under current coolant temperature is obtained
Required time；Wherein, maintaining cold start revolving speed required time corresponding under current coolant temperature is 10s-30s；
Step S3: it according to cold start revolving speed corresponding under current coolant temperature, obtains maintaining current coolant temperature
The friction torque of lower corresponding cold start revolving speed；It is turned round according to the friction of cold start revolving speed corresponding under current coolant temperature
Square, diesel oil starts distributive value 1 when determining cold start dual fuel engine；
Step S4: according to current coolant temperature, and cold start revolving speed corresponding under current coolant temperature determines
Diesel oil starts diesel oil in distributive value 2 and main jet and starts distributive value 3 in pre- spray；
Step S5: diesel oil in distributive value 1, in advance spray is started according to diesel oil when cold start dual fuel engine and starts distributive value 2
Diesel oil in spraying after distributive value 3 determines is started with diesel oil in main jet starts distributive value 4；
Step S6: if the ratio of diesel oil starting distributive value 4 and presently described rear spray number i spray after being more than or equal in rear spray
Minimum diesel oil starting distributive value 5, the rear number that sprays is presently described rear spray number i；Otherwise, spray number is i-1 afterwards；Wherein, i=2-
4；
Step S7: according to cold start revolving speed corresponding under current coolant temperature, according to the current coolant temperature of maintenance
Started the time required to lower corresponding cold start revolving speed, according to determining diesel oil distributive value 1, in pre- spray diesel oil start distributive value 2,
In main jet diesel oil start distributive value 3 and after spray number, cold start dual fuel engine, until automobile is in idle running shape
State, and when idle state, the revolving speed of dual fuel engine is 600rpm-800rpm.
Wherein, when cold start dual fuel engine, the process of diesel oil is started needed for nozzle injection successively by pre- spray, main jet
With rear spray three phases；Diesel oil starts distributive value 1 and starts 2 He of distributive value greater than diesel oil in pre- spray when cold start dual fuel engine
Diesel oil starts the sum of distributive value 3 in main jet；And rear spray number i is 2-4 times；
Referring to Fig. 3, the rear number i that sprays is according to lower section according to the size relation of current coolant temperature and environment temperature
Method is selected:
Under Current Temperatures, if diesel oil starts distributive value 4 in rear spray and the ratio of presently described rear spray number i is more than or equal to
Minimum diesel oil starting distributive value 5 is sprayed afterwards, and the rear number that sprays is presently described rear spray number i；Otherwise, the rear spray number is i-1.
The various restrictions occurred in the optimum embodiment are analyzed in the aforementioned embodiment, are no longer done and are further gone to live in the household of one's in-laws on getting married herein
It states.
The foregoing is merely illustrative of the preferred embodiments of the present invention, is not intended to limit the invention, all in essence of the invention
Within mind and principle, any modification, equivalent replacement, improvement and so on be should all be included in the protection scope of the present invention.
Claims (10)
1. a kind of dual fuel engine control method of cold start, which comprises the following steps:
Step S1: according to coolant temperature current in dual fuel engine, corresponding under current coolant temperature cold is obtained
Turn speed；Wherein, the cold start revolving speed corresponding under current coolant temperature is higher than current coolant temperature cold start bavin
Revolving speed corresponding to oil turbine, the double fuel are gasoline and diesel oil；
Step S2: the cold start revolving speed corresponding under the current coolant temperature, cold start dual fuel engine, until
Automobile is in idle state.
2. dual fuel engine control method of cold start according to claim 1, which is characterized in that in the step S1,
Corresponding cold start revolving speed is 1500rpm-2500rpm under the current coolant temperature.
3. dual fuel engine control method of cold start according to claim 1 or 2, which is characterized in that the step S1
Further include: according to the current coolant temperature, obtain the cold start revolving speed for remaining corresponding under the current coolant temperature
Required time, when executing the step S2, according to needed for the cold start revolving speed for remaining corresponding under the current coolant temperature
Time, cold start dual fuel engine.
4. dual fuel engine control method of cold start according to claim 3, which is characterized in that remain described current cold
It but is 10s-30s the time required to cold start revolving speed corresponding at a temperature of liquid.
5. dual fuel engine control method of cold start according to claim 1 or 2, which is characterized in that the step S2
In, before cold start dual fuel engine, determine that diesel oil starts distributive value (1) with the following method, then according to determining institute
It states diesel oil and starts distributive value (1), cold start dual fuel engine:
According to cold start revolving speed corresponding under the current coolant temperature, obtain maintaining institute under the current coolant temperature
The friction torque of corresponding cold start revolving speed；It is turned round according to the friction of cold start revolving speed corresponding under the current coolant temperature
Square, diesel oil starts distributive value (1) when determining the cold start dual fuel engine.
6. dual fuel engine control method of cold start according to claim 5, which is characterized in that in the step S2,
When cold start dual fuel engine, nozzle injection needed for start diesel oil process successively by spraying in advance, main jet and after spray three ranks
Section；Wherein, spray number is 2-4 times afterwards.
7. dual fuel engine control method of cold start according to claim 6, which is characterized in that after in the step S2
The number of spray selects in accordance with the following methods:
Under Current Temperatures, if it is described after spray in diesel oil start distributive value (4) and it is presently described after spray number i ratio be greater than etc.
In rear spray minimum diesel oil starting distributive value (5), it is presently described rear spray number i that number is sprayed after described；Otherwise, the rear spray number
For i-1.
8. dual fuel engine control method of cold start according to claim 6, which is characterized in that in the step S2,
Before cold start dual fuel engine, diesel oil starts diesel oil in distributive value (2) and the main jet and starts distributive value in the pre- spray
It (3) is determined according to cold start revolving speed corresponding under the current coolant temperature and the current coolant temperature
, when executing the step S2, diesel oil in distributive value (2) and the main jet is started according to diesel oil in pre- spray and starts distributive value (3),
Cold start dual fuel engine.
9. dual fuel engine control method of cold start a method according to any one of claims 6-8, which is characterized in that described
When cold start dual fuel engine, diesel oil starts distributive value (1) and is greater than diesel oil starting distributive value (2) and the master in the pre- spray
Diesel oil starts the sum of distributive value (3) in spray.
10. dual fuel engine control method of cold start according to claim 1 or 2, which is characterized in that the step S2
In, when the automobile is in idle state, the revolving speed of the dual fuel engine is 600rpm-800rpm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510282518.3A CN106285970B (en) | 2015-05-28 | 2015-05-28 | A kind of dual fuel engine control method of cold start |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510282518.3A CN106285970B (en) | 2015-05-28 | 2015-05-28 | A kind of dual fuel engine control method of cold start |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106285970A CN106285970A (en) | 2017-01-04 |
| CN106285970B true CN106285970B (en) | 2019-01-29 |
Family
ID=57634870
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510282518.3A Active CN106285970B (en) | 2015-05-28 | 2015-05-28 | A kind of dual fuel engine control method of cold start |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106285970B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110425047B (en) * | 2019-07-18 | 2021-12-21 | 潍柴动力股份有限公司 | Starting method and device of dual-fuel engine |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5027779A (en) * | 1989-08-29 | 1991-07-02 | Mitsubishi Denki Kabushiki Kaisha | Fuel injection control apparatus for an internal combustion engine |
| CN101387255A (en) * | 2008-10-20 | 2009-03-18 | 奇瑞汽车股份有限公司 | Low-temperature cold-start control method for diesel engine with heater plug |
| JP2010190067A (en) * | 2009-02-16 | 2010-09-02 | Yanmar Co Ltd | Engine |
| CN101984234A (en) * | 2010-11-11 | 2011-03-09 | 东莞传动电喷科技有限公司 | Control method of methanol/gasoline dual-fuel engine system |
| CN102278189A (en) * | 2011-04-28 | 2011-12-14 | 上海交通大学 | Direct injection engine with diesel-gasoline dual-fuel sequence combustion |
| JP2012189034A (en) * | 2011-03-11 | 2012-10-04 | Yanmar Co Ltd | Engine |
| CN104153891A (en) * | 2014-07-30 | 2014-11-19 | 长城汽车股份有限公司 | Diesel-petro engine start control system and method |
-
2015
- 2015-05-28 CN CN201510282518.3A patent/CN106285970B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5027779A (en) * | 1989-08-29 | 1991-07-02 | Mitsubishi Denki Kabushiki Kaisha | Fuel injection control apparatus for an internal combustion engine |
| CN101387255A (en) * | 2008-10-20 | 2009-03-18 | 奇瑞汽车股份有限公司 | Low-temperature cold-start control method for diesel engine with heater plug |
| JP2010190067A (en) * | 2009-02-16 | 2010-09-02 | Yanmar Co Ltd | Engine |
| CN101984234A (en) * | 2010-11-11 | 2011-03-09 | 东莞传动电喷科技有限公司 | Control method of methanol/gasoline dual-fuel engine system |
| JP2012189034A (en) * | 2011-03-11 | 2012-10-04 | Yanmar Co Ltd | Engine |
| CN102278189A (en) * | 2011-04-28 | 2011-12-14 | 上海交通大学 | Direct injection engine with diesel-gasoline dual-fuel sequence combustion |
| CN104153891A (en) * | 2014-07-30 | 2014-11-19 | 长城汽车股份有限公司 | Diesel-petro engine start control system and method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106285970A (en) | 2017-01-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| RU2629791C2 (en) | Engine operation method and engine system | |
| CN104100396A (en) | Method and system for engine control | |
| CN101498266B (en) | High pressure pump actuation in a vehicle | |
| CN103291481B (en) | A kind of pre-spray controlling method of motor, device and electrical control system for engine | |
| CN104153891A (en) | Diesel-petro engine start control system and method | |
| CN102619636B (en) | A kind of petrol engine energy-saving and emission-reduction combustion method | |
| CN106285970B (en) | A kind of dual fuel engine control method of cold start | |
| Isenstadt et al. | Naturally aspirated gasoline engines and cylinder deactivation | |
| CN105971752A (en) | Control unit for a multi-cylinder internal combustion engine | |
| CN103147892A (en) | Method for directly starting four-cylinder gasoline direct inject engine | |
| JP5776681B2 (en) | engine | |
| CN106150709A (en) | The idle speed control of dual fuel engine, system and vehicle | |
| CN106133298B (en) | Inject fuel into the method in internal combustion engine | |
| US11739710B2 (en) | Controller and method for controlling operation of a direct injection internal combustion engine | |
| JP5910176B2 (en) | Start control device for compression self-ignition engine | |
| JP5842678B2 (en) | Start control method and apparatus for compression self-ignition engine | |
| US11767800B2 (en) | Controller and a method for controlling an internal combustion engine | |
| Lee et al. | Analysis of the effect of cold start on fuel economy of gasoline automatic transmission vehicle | |
| CN106640385B (en) | Dual fuel engine accelerates control method, control device, engine and vehicle | |
| JP2014156852A (en) | Compression ignition engine | |
| JP5879965B2 (en) | Start control device for compression self-ignition engine | |
| JP5012594B2 (en) | Internal combustion engine | |
| CN103649500B (en) | Mobile engine starts control gear | |
| Teetz et al. | MTU HCCI engine with low raw emissions | |
| JP2018053732A (en) | Engine control device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |