CN104405548A - Vehicle, gasoline and diesel dual-fuel engine and fuel injection method thereof - Google Patents
Vehicle, gasoline and diesel dual-fuel engine and fuel injection method thereof Download PDFInfo
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- CN104405548A CN104405548A CN201410594231.XA CN201410594231A CN104405548A CN 104405548 A CN104405548 A CN 104405548A CN 201410594231 A CN201410594231 A CN 201410594231A CN 104405548 A CN104405548 A CN 104405548A
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- 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
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Abstract
The invention provides a vehicle, a gasoline and diesel dual-fuel engine and a fuel injection method thereof. Each working cycle comprises an intake stroke, a compression stroke, a working stroke and an exhaust stroke. The fuel injection method comprises the following steps of injecting a first predetermined fuel injection quantity D1 of pilot injection diesel into a cylinder in the compression stroke; next injecting a second predetermined fuel injection quantity G1 of main injection gasoline into the cylinder before the working stroke; then injecting a third predetermined fuel injection quantity D2 of main injection diesel into the cylinder in the working stroke; injecting a fourth predetermined fuel injection quantity G2 of post-injection gasoline into the cylinder after the injection of the main injection diesel and before the exhaust stroke, wherein D1 is smaller than D2, G1 is greater than or equal to G2, and G1 is smaller than D2. According to the gasoline and diesel dual-fuel engine and the fuel injection method thereof, the low-speed external characteristic of the engine is improved while the power and the torque of a high-speed region are not scarified.
Description
Technical field
The present invention relates to technical field of engines, particularly a kind of fuel injecting method of gasoline, diesel duel fuel engine, gasoline, diesel duel fuel engine and there is the vehicle of this gasoline, diesel duel fuel engine.
Background technique
In correlation technique, the method that diesel engine promotes low speed external characteristics is again matched with pressurization device, sacrifices high velocity power and moment of torsion, and diesel engine adopts main pre-spray twice jet mode, slow-speed of revolution exhaust energy is not enough, causes efficiency of turbocharger low, oil consumption is high and discharge is poor, there is room for improvement.
Summary of the invention
In view of this, the present invention is intended to the fuel injecting method proposing a kind of gasoline, diesel duel fuel engine, to promote the low speed external characteristics of motor while the power of not sacrificing high velocity and moment of torsion.
For achieving the above object, technological scheme of the present invention is achieved in that
A kind of fuel injecting method of gasoline, diesel duel fuel engine, each work cycle comprises intake stroke, compression stroke, expansion space stroke and exhaust stroke, described fuel injecting method comprises the following steps: in described compression stroke, the pre-spray diesel oil of the first predetermined fuel injection quantity D1 is sprayed into cylinder, before described expansion space stroke, the main jet gasoline of the second predetermined fuel injection quantity G1 is sprayed into described cylinder afterwards, then at described expansion space stroke, the main jet diesel oil of the 3rd predetermined fuel injection quantity D2 is sprayed into described cylinder, and injection described main jet diesel oil after and before described exhaust stroke, the rear spray gasoline of the 4th predetermined fuel injection quantity G2 is sprayed into described cylinder, wherein, D1 < D2, G1 >=G2, G1 < D2.
Further, when the front 25 DEG C of A-40 DEG C of A of piston arrives compression stroke top dead center, the pre-spray diesel oil of described first predetermined fuel injection quantity D1 is sprayed into described cylinder, when described piston arrives compression stroke top dead center front 5 DEG C of A-15 DEG C of A, the main jet gasoline of described second predetermined fuel injection quantity G1 is sprayed into described cylinder afterwards, then when described piston arrives expansion space stroke atdc 8 DEG C of A-12 DEG C of A, the main jet diesel oil of described 3rd predetermined fuel injection quantity D2 is sprayed into described cylinder, finally when described piston arrives expansion space stroke atdc 15 DEG C of A-25 DEG C of A, the rear spray gasoline of described 4th predetermined fuel injection quantity G2 is sprayed into described cylinder.
Preferably, when the front 30 DEG C of A of described piston arrives compression stroke top dead center, the pre-spray diesel oil of described first predetermined fuel injection quantity D1 is sprayed into described cylinder.
Preferably, when described piston arrives compression stroke top dead center front 10 DEG C of A, the main jet gasoline of described second predetermined fuel injection quantity G1 is sprayed into described cylinder.
Preferably, when piston arrives expansion space stroke atdc 10 DEG C of A, the main jet diesel oil of described 3rd predetermined fuel injection quantity D2 is sprayed into described cylinder.
Preferably, when piston arrives expansion space stroke atdc 20 DEG C of A, the rear spray gasoline of described 4th predetermined fuel injection quantity G2 is sprayed into described cylinder.
Further, described first predetermined fuel injection quantity D1 is 1 milligram/circulation-2 milligrams/circulation, described second predetermined fuel injection quantity G1 is 5 milligrams/circulation-15 milligrams/circulation, described 3rd predetermined fuel injection quantity D2 is 25 milligrams/circulation-35 milligrams/circulation, and described 4th predetermined fuel injection quantity G2 is 3 milligrams/circulation-5 milligrams/circulation.
Preferably, described second predetermined fuel injection quantity is 8 milligrams/circulation-10 milligrams/circulation.
Relative to prior art, of the present invention have following advantage:
(1) fuel injecting method of gasoline, diesel duel fuel engine of the present invention, by two kinds of fuel (namely being sprayed diesel oil in advance according to predetermined fuel injection quantity and predetermined oil spout order in each work cycle, main jet gasoline, main jet diesel oil, the oil spout order of rear spray gasoline) spray into cylinder, gasoline blending amount is increased, and form multi-point spark owing to spraying diesel combustion in advance, and the feature that gasoline combustion speed is fast, make in the continuous heat release of near top dead center, the thermal efficiency significantly improves, oil consumption obviously declines, not only improve low speed external characteristics, and maintain power and the moment of torsion of high velocity.
Another object of the present invention is to propose a kind of gasoline, diesel duel fuel engine, to reduce oil consumption, optimize discharge, promote low speed external characteristics and the power of maintenance high velocity and moment of torsion.
For achieving the above object, technological scheme of the present invention is achieved in that
A kind of gasoline, diesel duel fuel engine comprises: cylinder block, has cylinder in described cylinder block, is provided with piston in described cylinder, and described piston is engaged in described cylinder along the center line of described cylinder movably, cylinder head, described cylinder head is arranged on the top of described cylinder block, oil nozzle, described oil nozzle to be located in described cylinder head and to be communicated with described cylinder, the pre-spray diesel oil (1) of 1 milligram/circulation-2 milligrams/circulation is sprayed into described cylinder when being provided in the front 25 DEG C of A-40 DEG C of A of described piston arrives compression stroke top dead center by described oil nozzle, when described piston arrives compression stroke top dead center front 5 DEG C of A-15 DEG C of A, the main jet gasoline (2) of 5 milligrams/circulation-15 milligrams/circulation is sprayed into described cylinder, when described piston arrives expansion space stroke atdc 8 DEG C of A-12 DEG C of A, the main jet diesel oil (3) of 25 milligrams/circulation-35 milligrams/circulation is sprayed into described cylinder, when described piston arrives expansion space stroke atdc 15 DEG C of A-25 DEG C of A, the rear spray gasoline (4) of 3 milligrams/circulation-5 milligrams/circulation is sprayed into described cylinder.
Relative to prior art, gasoline, diesel duel fuel engine of the present invention has following advantage:
(1) gasoline, diesel duel fuel engine of the present invention carries out oil spout with specific oil spout order, fuel injection quantity and oil injection time, effectively improve the low speed external characteristics of duel fuel engine, and oil consumption is low, discharges.
Another object of the present invention is to propose a kind of vehicle, and described vehicle comprises the gasoline, diesel duel fuel engine described in above-described embodiment.
The Dominant Facies that described vehicle and above-mentioned gasoline, diesel duel fuel engine have relative to prior art is same, does not repeat them here.
Accompanying drawing explanation
The accompanying drawing forming a part of the present invention is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the flow chart of the fuel injecting method of the gasoline, diesel duel fuel engine described in the embodiment of the present invention.
Fig. 2 for utilizing the fuel injecting method of the gasoline, diesel duel fuel engine described in the embodiment of the present invention when change the 3rd predetermined instant, cylinder pressure changing trend diagram.
Fig. 3 is for utilizing the pattern Maximum Torque of the fuel injecting method oil spout of the gasoline, diesel duel fuel engine described in the embodiment of the present invention and pure diesel fuel mode Maximum Torque cylinder pressure comparison diagram.
Fig. 4 is for utilizing the pattern Maximum Torque of the fuel injecting method oil spout of the gasoline, diesel duel fuel engine described in the embodiment of the present invention and pure diesel fuel mode Max. torque rate of heat release comparison diagram.
Fig. 5 is for utilizing the pattern of the fuel injecting method oil spout of the gasoline, diesel duel fuel engine described in the embodiment of the present invention and pure diesel fuel mode low speed external characteristics comparison of test results figure.
Description of reference numerals:
Cylinder when 11-the 3rd predetermined instant is budc 2 DEG C of A is buckled line,
Cylinder when 12-the 3rd predetermined instant is atdc 4 DEG C of A is buckled line,
Cylinder when 13-the 3rd predetermined instant is atdc 10 DEG C of A is buckled line,
21-utilizes the cylinder pressure of the pattern Maximum Torque of the fuel injecting method oil spout of the gasoline, diesel duel fuel engine described in the embodiment of the present invention,
22-pure diesel fuel mode Maximum Torque cylinder pressure,
31-utilizes the rate of heat release of the pattern Maximum Torque of the fuel injecting method oil spout of the gasoline, diesel duel fuel engine described in the embodiment of the present invention,
32-pure diesel fuel mode Maximum Torque rate of heat release,
41-utilizes the low speed external characteristic curve of the pattern of the fuel injecting method oil spout of the gasoline, diesel duel fuel engine described in the embodiment of the present invention,
The low speed external characteristic curve of the pure diesel fuel mode of 42-,
1-sprays diesel oil in advance,
2-main jet gasoline,
3-main jet diesel oil,
Gasoline is sprayed after 4-.
Embodiment
It should be noted that, when not conflicting, the embodiment in the present invention and the feature in embodiment can combine mutually.
1-Fig. 5 also describes the present invention in detail in conjunction with the embodiments below with reference to the accompanying drawings.Each work cycle of gasoline, diesel duel fuel engine comprises intake stroke, compression stroke, expansion space stroke and exhaust stroke.
As shown in Figure 1, comprise the following steps according to the fuel injecting method of the gasoline, diesel duel fuel engine of the embodiment of the present invention:
In described compression stroke, the pre-spray diesel oil 1 of the first predetermined fuel injection quantity D1 is sprayed into cylinder, before described expansion space stroke, the main jet gasoline 2 of the second predetermined fuel injection quantity G1 is sprayed into cylinder afterwards, then at expansion space stroke, the main jet diesel oil 3 of the 3rd predetermined fuel injection quantity D2 is sprayed into cylinder, and injection described main jet diesel oil 3 after and before described exhaust stroke, the rear spray gasoline 4 of the 4th predetermined fuel injection quantity G2 is sprayed into cylinder, wherein, D1 < D2, G1 >=G2, G1 < D2.
That is, according to the fuel injecting method of the gasoline, diesel duel fuel engine of the embodiment of the present invention, in each work cycle, all successively by spraying diesel oil 1 in advance, main jet gasoline 2, main jet diesel oil 3, rear spray gasoline 4 sprays into cylinder according to respective predetermined fuel injection quantity, and the pre-spray diesel oil 1 of corresponding predetermined fuel injection quantity and main jet gasoline 2 successively spray into cylinder in compression stroke, the main jet diesel oil 3 of corresponding predetermined fuel injection quantity and rear spray gasoline 4 successively spray into cylinder at expansion space stroke.
In other words, each work cycle, gasoline and diesel oil two kinds of fuel alternately spray into cylinder, and gasoline twice injection, diesel oil twice injection, namely in this fuel injecting method, fuel is divided into four times and sprays into cylinder.
Like this, in described compression stroke, the pre-spray diesel oil 1 of the first predetermined fuel injection quantity D1 is sprayed into cylinder, reduce combustion noise on the one hand, on the other hand for subsequent combustion burning creates suitable ambient temperature to promote the burning of the follow-up main jet gasoline 2 sprayed into, play the effect being similar to plug ignition, and be multi-point spark.
In described compression stroke, after spraying pre-spray diesel oil 1, the main jet gasoline 2 of the second predetermined fuel injection quantity G1 is sprayed into cylinder, because main jet gasoline 2 combustion heat release is fast, on the basis promoting a part of moment of torsion, improve the thermal efficiency, thus improve the fuel economy of motor.
At described expansion space stroke, the main jet diesel oil 3 of the 3rd predetermined fuel injection quantity D2 is sprayed into cylinder, plays the leading role of increasing productivity, that is, the main jet diesel oil 3 of the 3rd predetermined fuel injection quantity D2 sprays into the most of moment of torsion of the contribute energy of cylinder after-combustion generation.
At described expansion space stroke, after spraying main jet diesel oil 3, the rear spray gasoline 4 of the 4th predetermined fuel injection quantity G2 is sprayed into cylinder, reduce smoke emission on the one hand, improve exhaust energy on the other hand, solve the problem of pressurized machine low speed response difference, thus improve new charge amount.
Due to D1 < D2, G1 >=G2, G1 < D2, be understandable that, moment of torsion is contributed primarily of the main jet diesel oil 3 of the 3rd predetermined fuel injection quantity D2, such as, in specific embodiments more of the present invention, the main jet diesel oil 3 of the 3rd predetermined fuel injection quantity D2 is the moment of torsion of low speed external characteristics contribution 50%, and the main jet gasoline 2 of the pre-spray diesel oil 1 of the first predetermined fuel injection quantity D1 and the second predetermined fuel injection quantity G1 is the moment of torsion that low speed external characteristics contributes 40%.
According to the fuel injecting method of the gasoline, diesel duel fuel engine of the embodiment of the present invention, by two kinds of fuel (namely being sprayed diesel oil 1 in advance according to predetermined fuel injection quantity and predetermined oil spout order in each work cycle, main jet gasoline 2, main jet diesel oil 3, the oil spout order of rear spray gasoline 4) spray into cylinder, gasoline blending amount is increased, and form multi-point spark owing to spraying diesel oil 1 burning in advance, and the feature that gasoline combustion speed is fast, in the continuous heat release of near top dead center, the thermal efficiency significantly improves, oil consumption obviously declines, not only improve low speed external characteristics, and maintain power and the moment of torsion of high velocity.
Be understandable that, the major parameter of the fuel injecting method of gasoline, diesel duel fuel engine is oil spout order, oil injection time and predetermined fuel injection quantity, after determining oil spout order, in order to optimize the fuel injecting method of gasoline, diesel duel fuel engine further, inventor has done lot of experiments, is optimized further oil injection time and predetermined fuel injection quantity by a large amount of experimental studies.
First optimize the pre-spray predetermined fuel injection quantity of diesel oil 1 and the predetermined fuel injection quantity of main jet gasoline 2, namely first coordinate the magnitude relationship of the first predetermined fuel injection quantity D1 and the second predetermined fuel injection quantity G1.
Wherein, if the first predetermined fuel injection quantity D1 is larger, then ignition energy is more sufficient, the second predetermined fuel injection quantity G1 is fewer, if but the first predetermined fuel injection quantity D1 is less, then ignition energy is not enough, in addition gasoline and new charge proportions of ingredients rarer, be unfavorable for the burning of gasoline, cause HC higher, combustion heat release cannot be embodied fast, fuel-efficient advantage.Further, along with the increase of the predetermined fuel injection quantity of main jet gasoline 2, namely the second predetermined fuel injection quantity G1 increases, and moment of torsion is large along with change, equally also makes the rate of pressure rise also increasing.
By above-mentioned analysis and lot of experiments, and consider the problem that combustion noise and load are expanded, controlling the first predetermined fuel injection quantity D1 is 1 milligram/circulation-2 milligrams/circulation, second predetermined fuel injection quantity G1 is 5 milligrams/circulation-15 milligrams/circulation, now the ratio of the first predetermined fuel injection quantity D1 and the second predetermined fuel injection quantity G1 is the most applicable, and ignition ability is sufficient, combustion heat release is fast and oil consumption is low.
Preferably, the second predetermined fuel injection quantity G1 is 8 milligrams/circulation-10 milligrams/circulation.
Further, the pre-spray oil injection time of diesel oil 1 and the oil injection time of main jet gasoline 2 is optimized.The experimental research a large amount of by inventor shows, when the front 25 DEG C of A-40 DEG C of A of piston arrives compression stroke top dead center, the pre-spray diesel oil 1 of the first predetermined fuel injection quantity D1 is sprayed into cylinder, when described piston arrives compression stroke top dead center front 5 DEG C of A-15 DEG C of A, the main jet gasoline 2 of described second predetermined fuel injection quantity G1 is sprayed into cylinder afterwards, can combustion noise be reduced and the premixing effect of gasoline, diesel is better.
Preferably, when the front 30 DEG C of A of piston arrives compression stroke top dead center, the pre-spray diesel oil 1 of the first predetermined fuel injection quantity D1 is sprayed into cylinder.
Preferably, when piston arrives compression stroke top dead center front 10 DEG C of A, the main jet gasoline 2 of the second predetermined fuel injection quantity G1 is sprayed into described cylinder.
Shown in the curve 13 of Fig. 2 and the curve 21 of Fig. 3, pre-spray diesel oil 1 and the heat release of main jet gasoline 2 co-fire form first exothermic peak, and first exothermic peak is in the budc of compression stroke, and main jet diesel oil 3 and the heat release of rear spray gasoline 4 co-fire form second exothermic peak, and second exothermic peak is in the atdc of compression stroke, thus according to the fuel injecting method of the gasoline, diesel duel fuel engine of the embodiment of the present invention, bimodal heat release is formed near top dead center, produce two mild cylinder pressures, thus promote low speed external characteristics load.Compared with pure diesel fuel mode, under identical detonation pressure and rate of pressure rise condition, the oil injection time of the main jet diesel oil under former pure diesel fuel mode sprays into main jet gasoline 2, and combustion heat release is fast, and the thermal efficiency is high and fuel consumption rate is low.
Further, optimize the oil injection time of main jet diesel oil 3, and optimize the predetermined fuel injection quantity of main jet diesel oil 3, namely optimize the 3rd predetermined fuel injection quantity D2.
With reference to shown in Fig. 2, the oil injection time (i.e. main jet timing) of the main jet diesel oil 3 of curve 11, curve 12 and curve 13 postpones gradually, and the fuel injection quantity of main jet diesel oil 3 increases gradually, therefore as shown in curve 13, second exothermic peak postpones, combustion duration is elongated, before whirlpool, temperature raises, and exhaust energy increase makes efficiency of turbocharger improve, and new charge amount increases, promote the burning in cylinder on the contrary, form a benign cycle.Form above-mentioned eucyclic concrete reason as follows: along with the increase of new charge amount, working medium in cylinder increases, the combustion phase of first combustion peak in advance, detonation pressure raises, and causes cylinder pressure to become bimodal (as shown in the curve 13 Fig. 2), although exhaust loss pumping loss increases from unimodal gradually, but heat transfer loss significantly reduces, IMEP (on average indicating in-cylinder pressure) increases, and the work done duration is elongated, finally makes moment of torsion increase.
Shown by the lot of experiments of inventor, when piston arrives expansion space stroke atdc 8 DEG C of A-12 DEG C of A, the main jet diesel oil 3 of the 3rd predetermined fuel injection quantity D2 is sprayed into cylinder, due to main jet diesel oil 3, to spray into cylinder more late, away from first exothermic peak that pre-spray diesel oil 1 and main jet gasoline 2 co-fire are formed, cylinder combustion burning temperature is low, the delay period of main jet diesel oil 3 is elongated, and smoke emission reduces.
Preferably, when piston arrives expansion space stroke atdc 10 DEG C of A, the main jet diesel oil 3 of the 3rd predetermined fuel injection quantity D2 is sprayed into cylinder.
Be understandable that, the combustion law of conventional diesel engine is, along with main jet timing postpones, smoke intensity and HC discharge are along with rising, and oil consumption obviously worsens.Found by the contrast of the combustion law with conventional diesel engine, according to the fuel injecting method of the gasoline, diesel duel fuel engine of the embodiment of the present invention, broken the combustion law of conventional diesel engine.
Specifically, the fuel injecting method in the present invention, after main jet timing postpones, while increasing productivity, oil consumption increases, but smoke emission has reduction trend on the contrary.Concrete reason is as follows: delivery temperature raises, and new charge amount increases, and reduces localized hyperthermia's anoxic zones, reduces the lift of soot.
Preferably, the 3rd predetermined fuel injection quantity D2 is 25 milligrams/circulation-35 milligrams/circulation, thus contributes 50% moment of torsion for low speed external characteristics.
Finally, optimize the predetermined fuel injection quantity of rear spray gasoline 4 further, namely optimize the 4th predetermined fuel injection quantity G2, and spray the oil injection time of gasoline 4 after optimizing.
When piston arrives expansion space stroke atdc 15 DEG C of A-25 DEG C of A, the rear spray gasoline 4 of the 4th predetermined fuel injection quantity G2 is sprayed into cylinder, in other words, during piston arrives expansion space stroke atdc 15 DEG C of A-25 DEG C of A, the predetermined fuel injection quantity of main jet diesel oil 3 has burnt 50%-90%, now introduce the rear spray gasoline 4 of the 4th predetermined fuel injection quantity G2, after-burning temperature can be improved, promote soot (soot that main jet diesel oil 3 burning produces) oxidation, keep lower smoke emission level, keep the efficiency of turbocharger that low velocity zone is higher simultaneously, final raising new charge amount, pumping loss is little, the thermal efficiency is high, fuel consumption rate is low, thus promote low speed load further.Wherein, the 4th predetermined fuel injection quantity G2 is 3 milligrams/circulation-5 milligrams/circulation.
Preferably, when piston arrives expansion space stroke atdc 20 DEG C of A, the rear spray gasoline 4 of described 4th predetermined fuel injection quantity G2 is sprayed into described cylinder.
Below in conjunction with Fig. 3, Fig. 4 and Fig. 5, analyze the fuel injecting method according to the gasoline, diesel duel fuel engine of the embodiment of the present invention and the contrast of pure diesel fuel mode in low speed external characteristics.
Known by the contrast of the curve 21 in Fig. 3 and curve 22, under pure diesel fuel mode, cylinder pressure is for unimodal, and when utilizing fuel injecting method oil spout of the present invention, cylinder pressure is for bimodal.
Known by the contrast of the curve 31 in Fig. 4 and curve 32, when utilizing fuel injecting method oil spout of the present invention, produce continuous heat release at the near top dead center of compression stroke, the thermal efficiency is apparently higher than pure diesel fuel mode.
That is, utilize the gasoline, diesel duel fuel engine of fuel injecting method oil spout of the present invention, make use of gasoline and diesel oil two kinds of fuel, the formation multi-point spark and pre-spray diesel oil 1 burns, adds that gasoline combustion speed is fast, in the continuous heat release of near top dead center, the thermal efficiency significantly improves, and oil consumption obviously reduces.
In addition, when utilizing fuel injecting method oil spout of the present invention, reserve factor λ is close to 1.That is, relative to pure diesel fuel mode, when utilizing fuel injecting method oil spout of the present invention, the new charge amount of low speed torque point demand can reduce, thus exhaust back pressure reduces, and finally makes fuel consumption rate decline.Wherein, λ=T1/T2, wherein T1 is the Maximum Torque under full load low-speed characteristic, and T2 is the moment of torsion under motor meets car load demand.
As shown in Figure 5, curve 41 utilizes the low speed external characteristic curve of the pattern of the fuel injecting method oil spout of the gasoline, diesel duel fuel engine described in the embodiment of the present invention, the oil spout order of curve 41 is pre-spray diesel oil 1, main jet gasoline 2, main jet diesel oil 3, rear spray gasoline 4 as we know from the figure, and curve 42 is the low speed external characteristic curve of pure diesel fuel mode, and oil spout order is pre-spray diesel oil 1, main jet diesel oil 3.
Known by the contrast of the curve 41 in Fig. 5 and curve 42, in smoke intensity limit value, fuel injecting method according to the present invention compares that pure diesel fuel mode moment of torsion is maximum can promote 20%, specifically, when engine speed is lower, moment of torsion when being greater than pure diesel fuel mode according to moment of torsion during fuel injecting method oil spout of the present invention.Along with the increase of engine speed, efficiency of turbocharger can increase, and close to the economic region of pure diesel fuel mode, burning confined condition broadens, and fuel injecting method advantage according to the present invention reduces gradually.
That is, according to the fuel injecting method of the gasoline, diesel duel fuel engine of the embodiment of the present invention, improve the low speed external characteristics of motor, and maintain power and the moment of torsion of high velocity.
Present invention also offers a kind of gasoline, diesel duel fuel engine.Described gasoline, diesel duel fuel engine comprises: cylinder block, cylinder head and oil nozzle.
Have cylinder in cylinder block, be provided with piston in cylinder, piston is engaged in cylinder along the center line of cylinder movably to complete intake stroke, compression stroke, expansion space stroke and exhaust stroke in each work cycle.
Cylinder head is arranged on the top of cylinder block, oil nozzle to be located in cylinder head and to be communicated with cylinder, the pre-spray diesel oil 1 of 1 milligram/circulation-2 milligrams/circulation is sprayed into cylinder when being provided in the front 25 DEG C of A-40 DEG C of A of piston arrives compression stroke top dead center by oil nozzle, when piston arrives compression stroke top dead center front 5 DEG C of A-15 DEG C of A, the main jet gasoline 2 of 5 milligrams/circulation-15 milligrams/circulation is sprayed into cylinder, when piston arrives expansion space stroke atdc 8 DEG C of A-12 DEG C of A, the main jet diesel oil 3 of 25 milligrams/circulation-35 milligrams/circulation is sprayed into cylinder, when piston arrives expansion space stroke atdc 15 DEG C of A-25 DEG C of A, the rear spray gasoline 4 of 3 milligrams/circulation-5 milligrams/circulation is sprayed into cylinder.
According to the gasoline, diesel duel fuel engine of the embodiment of the present invention, carry out oil spout with specific oil spout order, fuel injection quantity and oil injection time, effectively improve the low speed external characteristics of duel fuel engine, and oil consumption is low, discharges.
Present invention also offers a kind of vehicle, this vehicle comprises the gasoline, diesel duel fuel engine described in above-described embodiment, thus it is low to have oil consumption, discharges, the advantage that low speed external characteristics effectively promotes.
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. a fuel injecting method for gasoline, diesel duel fuel engine, is characterized in that, each work cycle comprises intake stroke, compression stroke, expansion space stroke and exhaust stroke, and described fuel injecting method comprises the following steps:
In described compression stroke, the pre-spray diesel oil (1) of the first predetermined fuel injection quantity D1 is sprayed into cylinder, before described expansion space stroke, the main jet gasoline (2) of the second predetermined fuel injection quantity G1 is sprayed into described cylinder afterwards, then at described expansion space stroke, the main jet diesel oil (3) of the 3rd predetermined fuel injection quantity D2 is sprayed into described cylinder, and injection described main jet diesel oil (3) after and before described exhaust stroke, the rear spray gasoline (4) of the 4th predetermined fuel injection quantity G2 is sprayed into described cylinder, wherein, D1 < D2, G1 >=G2, G1 < D2.
2. the fuel injecting method of gasoline, diesel duel fuel engine according to claim 1, is characterized in that,
When the front 25 DEG C of A-40 DEG C of A of piston arrives compression stroke top dead center, the pre-spray diesel oil (1) of described first predetermined fuel injection quantity D1 is sprayed into described cylinder,
When described piston arrives compression stroke top dead center front 5 DEG C of A-15 DEG C of A, the main jet gasoline (2) of described second predetermined fuel injection quantity G1 is sprayed into described cylinder afterwards,
Then when described piston arrives expansion space stroke atdc 8 DEG C of A-12 DEG C of A, the main jet diesel oil (3) of described 3rd predetermined fuel injection quantity D2 is sprayed into described cylinder,
Finally when described piston arrives expansion space stroke atdc 15 DEG C of A-25 DEG C of A, the rear spray gasoline (4) of described 4th predetermined fuel injection quantity G2 is sprayed into described cylinder.
3. the fuel injecting method of gasoline, diesel duel fuel engine according to claim 2, is characterized in that,
When the front 30 DEG C of A of described piston arrives compression stroke top dead center, the pre-spray diesel oil (1) of described first predetermined fuel injection quantity D1 is sprayed into described cylinder.
4. the fuel injecting method of gasoline, diesel duel fuel engine according to claim 2, is characterized in that,
When described piston arrives compression stroke top dead center front 10 DEG C of A, the main jet gasoline (2) of described second predetermined fuel injection quantity G1 is sprayed into described cylinder.
5. the fuel injecting method of gasoline, diesel duel fuel engine according to claim 2, is characterized in that, when piston arrives expansion space stroke atdc 10 DEG C of A, the main jet diesel oil (3) of described 3rd predetermined fuel injection quantity D2 is sprayed into described cylinder.
6. the fuel injecting method of gasoline, diesel duel fuel engine according to claim 2, is characterized in that, when piston arrives expansion space stroke atdc 20 DEG C of A, the rear spray gasoline (4) of described 4th predetermined fuel injection quantity G2 is sprayed into described cylinder.
7. the fuel injecting method of gasoline, diesel duel fuel engine according to claim 1 and 2, is characterized in that,
Described first predetermined fuel injection quantity D1 is 1 milligram/circulation-2 milligrams/circulation, described second predetermined fuel injection quantity G1 is 5 milligrams/circulation-15 milligrams/circulation, described 3rd predetermined fuel injection quantity D2 is 25 milligrams/circulation-35 milligrams/circulation, and described 4th predetermined fuel injection quantity G2 is 3 milligrams/circulation-5 milligrams/circulation.
8. the fuel injecting method of gasoline, diesel duel fuel engine according to claim 7, is characterized in that,
Described second predetermined fuel injection quantity is 8 milligrams/circulation-10 milligrams/circulation.
9. a gasoline, diesel duel fuel engine, is characterized in that, comprising:
Cylinder block, has cylinder in described cylinder block, is provided with piston in described cylinder, and described piston is engaged in described cylinder along the center line of described cylinder movably;
Cylinder head, described cylinder head is arranged on the top of described cylinder block;
Oil nozzle, described oil nozzle to be located in described cylinder head and to be communicated with described cylinder, the pre-spray diesel oil (1) of 1 milligram/circulation-2 milligrams/circulation is sprayed into described cylinder when being provided in the front 25 DEG C of A-40 DEG C of A of described piston arrives compression stroke top dead center by described oil nozzle, when described piston arrives compression stroke top dead center front 5 DEG C of A-15 DEG C of A, the main jet gasoline (2) of 5 milligrams/circulation-15 milligrams/circulation is sprayed into described cylinder, when described piston arrives expansion space stroke atdc 8 DEG C of A-12 DEG C of A, the main jet diesel oil (3) of 25 milligrams/circulation-35 milligrams/circulation is sprayed into described cylinder, when described piston arrives expansion space stroke atdc 15 DEG C of A-25 DEG C of A, the rear spray gasoline (4) of 3 milligrams/circulation-5 milligrams/circulation is sprayed into described cylinder.
10. a vehicle, is characterized in that, comprises gasoline, diesel duel fuel engine according to claim 9.
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| CN201410594231.XA CN104405548B (en) | 2014-10-29 | 2014-10-29 | Vehicle, gasoline, diesel dual fuel engine and its fuel injecting method |
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| CN201410594231.XA CN104405548B (en) | 2014-10-29 | 2014-10-29 | Vehicle, gasoline, diesel dual fuel engine and its fuel injecting method |
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| CN110344955A (en) * | 2018-04-03 | 2019-10-18 | 丰田自动车株式会社 | The control device of internal combustion engine |
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| CN1821561A (en) * | 2005-02-17 | 2006-08-23 | 通用汽车公司 | Compression-ignited ic engine and method of operation |
| US20070256648A1 (en) * | 2006-05-08 | 2007-11-08 | Harold Sun | Controlling engine operation with a first and second fuel |
| CN103161563A (en) * | 2011-12-15 | 2013-06-19 | 现代自动车株式会社 | Dual fuel combustion system based on diesel compression ignition triggered ignition control |
| US20140026853A1 (en) * | 2012-07-25 | 2014-01-30 | Charles L. Gray, Jr. | Low Temperature Dual Fuel Combustion Utilizing Diesel and Methanol Fuels |
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| CN1821561A (en) * | 2005-02-17 | 2006-08-23 | 通用汽车公司 | Compression-ignited ic engine and method of operation |
| US20070256648A1 (en) * | 2006-05-08 | 2007-11-08 | Harold Sun | Controlling engine operation with a first and second fuel |
| CN103161563A (en) * | 2011-12-15 | 2013-06-19 | 现代自动车株式会社 | Dual fuel combustion system based on diesel compression ignition triggered ignition control |
| US20140026853A1 (en) * | 2012-07-25 | 2014-01-30 | Charles L. Gray, Jr. | Low Temperature Dual Fuel Combustion Utilizing Diesel and Methanol Fuels |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110344955A (en) * | 2018-04-03 | 2019-10-18 | 丰田自动车株式会社 | The control device of internal combustion engine |
| CN110344955B (en) * | 2018-04-03 | 2022-07-08 | 丰田自动车株式会社 | Control device for internal combustion engine |
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