CN105317573A - Fuel injection method for direct injection combustion system - Google Patents
Fuel injection method for direct injection combustion system Download PDFInfo
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- CN105317573A CN105317573A CN201410268140.7A CN201410268140A CN105317573A CN 105317573 A CN105317573 A CN 105317573A CN 201410268140 A CN201410268140 A CN 201410268140A CN 105317573 A CN105317573 A CN 105317573A
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- 238000002347 injection Methods 0.000 title claims abstract description 56
- 239000007924 injection Substances 0.000 title claims abstract description 56
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 50
- 238000000034 method Methods 0.000 title claims abstract description 28
- 239000000446 fuel Substances 0.000 title claims abstract description 26
- 239000007921 spray Substances 0.000 claims abstract description 44
- 238000010304 firing Methods 0.000 claims description 24
- 239000003595 mist Substances 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 108
- 238000005507 spraying Methods 0.000 description 18
- 230000000694 effects Effects 0.000 description 9
- 239000000203 mixture Substances 0.000 description 6
- 238000001704 evaporation Methods 0.000 description 5
- 230000008020 evaporation Effects 0.000 description 5
- 239000000295 fuel oil Substances 0.000 description 5
- 239000007789 gas Substances 0.000 description 5
- 238000010348 incorporation Methods 0.000 description 5
- 238000000889 atomisation Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 4
- 239000002245 particle Substances 0.000 description 4
- 238000010790 dilution Methods 0.000 description 3
- 239000012895 dilution Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000005474 detonation Methods 0.000 description 2
- 230000035515 penetration Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000004888 barrier function Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010721 machine oil Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012805 post-processing Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 239000002912 waste gas Substances 0.000 description 1
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- Fuel-Injection Apparatus (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
The invention relates to a fuel injection method for a direct injection combustion system. A spark plug and two fuel injectors of the direct injection combustion system are all located in a middle area on the top of a combustion chamber. The two fuel injectors are symmetrically arranged on the two sides of the spark plug. Fuel spray injected by the fuel injectors does not interfere with the spark plug, and the fuel spray injected by the two fuel injectors does not interfere with each other. Under the working condition that an engine operates at a large load, the two fuel injectors are controlled to conduct injection simultaneously in the air-intake stroke; under the working condition that the engine operates at a medium or small load, the two fuel injectors are controlled to conduct injection alternately or intermittently and alternately in the air-intake stroke. Under different working conditions, the flow coefficient of mist can be adjusted while the injection pressure is ensured, and the requirements of the corresponding working conditions are met.
Description
Technical field
The present invention relates to vehicular field, be specifically related to a kind of fuel-injecting method for in-cylinder direct injection combustion system.
Background technique
Motor is the vitals in automobile, and the transformation of energy of a certain form is provided power for mechanical energy exports to automobile by it.
As shown in Figure 1-2, motor comprises cylinder 5, and cylinder 5 top has cylinder head 6, is connected with bent axle 8 bottom cylinder 5, and piston 7 is connected to bent axle 8 top, and piston 7 makes iterative motion along with the rotation of bent axle 8 in cylinder 5; More than piston 7 end face, the space formed below cylinder head 6 bottom surface is called firing chamber; Cylinder head 6 is connected with intake duct 3, air outlet flue 4, oil sprayer 1 and spark plug 2, intake duct 3 and air outlet flue 4 are respectively at combustion chamber, and oil sprayer 1 all stretches into firing chamber with the head of spark plug 2.Wherein firing chamber and all parts of being connected to firing chamber are referred to as combustion system.
In-cylinder direct injection combustion system is the one of combustion system, in China, by the impact of fuel qualities and post-processing technology, and the increasing proportion that in-cylinder direct injection combustion system takies in the market.The arrangement of in-cylinder direct injection combustion system mainly contains two kinds, and the first oil sprayer 1 is arranged in the opposite side (namely intake duct 3 outside) of intake duct 3 relative to air outlet flue 4, adopts side direction to spray, as shown in Figure 1; The second is that oil sprayer 1 is arranged in the zone line of cylinder head 6 between intake duct 3 and air outlet flue 4, adopts central-injection, as shown in Figure 2.
Under desirable state, when motor runs under high rotating speed high load working condition, the amount of fuel that sprays in cylinder of often circulating is larger, wish that the flow coefficient of oil sprayer can improve as far as possible, spray into as soon as possible in cylinder in intake process to realize a large amount of fuel oils, leave enough evaporation incorporation times, reach the effect of best Homogeneous phase mixing burning; When motor runs under middle small load condition, the amount of fuel that sprays in cylinder of often circulating is considerably less, and incorporation time is relatively more abundant, wishes that again the flow coefficient of oil sprayer can reduce as far as possible, with the discharge time of proper extension fuel oil in intake process, improve the operation stability of oil sprayer.
Therefore, when selecting oil sprayer, just there is one group of above-mentioned contradiction in motor (especially Homogeneous phase mixing in-cylinder direct fuel-injection engine), thus the state that cannot realize ideal.In order to solve the problem, prior art have employed the method for compromise: select the oil sprayer that flow coefficient is placed in the middle.But this can come again with new problem: when running under high rotating speed high load working condition, because fuel injector flow coefficient is large not, extends fuel injection time, decrease the evaporation incorporation time of spraying, reduce the uniformity of air-fuel mixture in cylinder to a certain extent, have impact on the effect of burning; When motor runs under middle small load condition, need the flow coefficient, the prolongation discharge time that reduce oil sprayer by reducing jet pressure, due to the reduction of jet pressure, the Mean particle diameter of spray particle can significantly increase, the atomizing effect of spraying is caused to reduce, also reduce the uniformity of air-fuel mixture in cylinder to a certain extent, have impact on combustion and emission.
Summary of the invention
The invention provides a kind of fuel-injecting method of in-cylinder direct injection combustion system.It can meet motor demand to mist flow under different operating mode, improves the atomization mixed effect of spraying, improves the uniformity of air-fuel mixture in cylinder, thus realizes more preferably burning, emission effect.
For solving the problem, the invention provides a kind of fuel-injecting method of in-cylinder direct injection combustion system, described in-cylinder direct injection combustion system comprises firing chamber, and described top of combustion chamber is connected with spark plug and oil sprayer;
Described spark plug and described oil sprayer are all positioned at the zone line of top of combustion chamber;
Described oil sprayer has two, is symmetricly set in described spark plug both sides;
Do not interfere between the oil bundle that described oil sprayer sprays and described spark plug, and do not interfere between the oil bundle of two oil sprayer injections;
Under the operating mode of motor large load operation, in aspirating stroke, control two described oil sprayers and spray simultaneously;
Under the operating mode that Smaller load runs within the engine, in aspirating stroke, control two described oil sprayers and spray in turn or intermittently spray in turn.
Optionally, under all operating modes of motor, the actual mixing ratio of oil inflame is close to chemically correct fuel.
Optionally, described oil sprayer stretches into the length in firing chamber is 5 ~ 10mm.
Optionally, the angle of described oil sprayer and described firing chamber axial direction is 5 ~ 10 degree.
Optionally, described oil sprayer is porous type oil sprayer.
Optionally, the spray orifice of described oil sprayer is 6 ~ 7, and the diameter of described spray orifice is 150 ~ 180 μm.
Optionally, described in-cylinder direct injection combustion system also comprises the intake duct and air outlet flue that are connected with described top of combustion chamber;
Described intake duct and described air outlet flue are arranged in outside the zone line of described top of combustion chamber respectively, and described intake duct is positioned at the side of two oil sprayers, and described air outlet flue is positioned at the opposite side of two oil sprayers.
Optionally, described intake duct and described air outlet flue all have two, and are arranged symmetrically with relative to described spark plug respectively.
Compared with prior art, technological scheme of the present invention has the following advantages:
Relative to prior art, present invention employs two oil sprayers and be arranged symmetrically in top of combustion chamber, do not destroy the feature of existing in-cylinder direct injection combustion system.The flow coefficient of each oil sprayer can select 65 ~ 70% of existing single oil sprayer, namely selects the oil sprayer that two a little bit smaller.Like this, under the operating conditions of the large load of motor, adopt the strategy that two oil sprayers spray simultaneously, overall flow coefficient can be improved, shorten fuel injection time, increase the evaporation of spraying, incorporation time, improve the uniformity of mixed gas in cylinder when lighting a fire, be conducive to combustion and emission; Under the operating conditions of Smaller load within the engine, (each oil sprayer sprays once to adopt two oil sprayers to spray in turn, two oil sprayers are used alternatingly) or interval is sprayed in turn, and (each oil sprayer sprays repeatedly, two oil sprayers are used alternatingly) strategy, fuel-injection pressure can be improved, promote the quality of spray atomization, increase the uniformity of mixed gas in cylinder, ensure better burning, emission effect.In addition, also increase the stability of oil sprayer working procedure, extend the working life of oil sprayer.
Accompanying drawing explanation
Fig. 1 is the structural representation of a kind of in-cylinder direct injection combustion system in prior art;
Fig. 2 is the structural representation of another kind of in-cylinder direct injection combustion system in prior art;
Fig. 3 is the structural representation of the in-cylinder direct injection combustion system of embodiment of the present invention fuel-injecting method;
Fig. 4 is the schematic top plan view of the in-cylinder direct injection combustion system of embodiment of the present invention fuel-injecting method;
Fig. 5 is the schematic cross-section of the main apparent direction of piston in the in-cylinder direct injection combustion system of embodiment of the present invention fuel-injecting method.
Embodiment
As described in the background art, when motor high load working condition runs and middle small load condition runs, completely different to the requirement of fuel injector flow system, and current in-cylinder direct injection system cannot meet above-mentioned two kinds of requirements simultaneously, so that desirable state can not be reached, therefore in the design of in-cylinder direct injection combustion system, the pattern of compromising can only be selected: adopt the oil sprayer that flow coefficient is placed in the middle.
When motor runs under high rotating speed high load working condition, spray into 100 ~ 120mg fuel oil in cylinder possibly in a cycle, and when the oil sprayer adopting flow coefficient placed in the middle, even if spray according to system peak injection pressure 150bar, course of injection also can continue 150 crank angles (namely bent axle turns over 150 degree) left and right, so, the incorporation time be sprayed in cylinder is easily caused to be shortened, cause the problem that air-fuel mixture is uneven and oil dilution amount is large, and oil dilution amount can cause the series of problems such as pre-ignition and super detonation greatly.
When motor runs under middle and slow speed of revolution small load condition, the amount of fuel sprayed in cylinder sometimes only has 10-20mg.If sprayed according to system peak injection pressure, oil sprayer discharge time can be very short, namely in oil sprayer needle-valve unlatching, the shut-in time can be very of short duration, fuel injector flow can be caused so unstable, and then affect the performance of oil sprayer.At present, in order to take precautions against this situation, as described in the background art, in working control, the way reducing jet pressure is generally taked, such as: reduce to 40-50bar by the jet pressure of 150bar.Although extend discharge time like this, because jet pressure reduces, cause the particle diameter of spraying to increase several times, correspondingly, the penetration degree of spraying is elongated, and atomization and evaporation are deteriorated, and finally cause the combustion stability of fuel oil to reduce.
The present invention is directed to the above-mentioned problems in the prior art, a kind of fuel-injecting method for in-cylinder direct injection combustion system is provided.
For enabling above-mentioned purpose of the present invention, feature and advantage more become apparent, and are described in detail specific embodiments of the invention below in conjunction with accompanying drawing.
The invention provides a kind of fuel-injecting method for in-cylinder direct injection combustion system, wherein adopt a kind of new in-cylinder direct injection combustion system, with reference to Fig. 3-4, in-cylinder direct injection combustion system comprises:
Primarily of the firing chamber 100 that cylinder 120, cylinder head 130 and piston 110 surround, top, described firing chamber 100 is connected with spark plug 102 and oil sprayer 101;
Described spark plug 102 and described oil sprayer 101 are all positioned at the zone line of top, firing chamber 100 cylinder head 130, here " zone line " refers to the region with certain limit be formed centrally in cylinder head 130, namely relatively near the region at cylinder head 130 center, absolute center is not referred to;
Described oil sprayer 101 has two, is symmetricly set in described spark plug 102 both sides;
Do not interfere between the oil bundle that described oil sprayer 101 sprays and described spark plug 102, and do not interfere between the oil bundle of two oil sprayer 101 injections.That is, the oil bundle 101a that oil sprayer 101 sprays can not be sprayed onto on spark plug 102, otherwise can affect the ignition performance of spark plug 102, can not occur intersecting between the oil bundle 101a of two oil sprayer 101 injections simultaneously, as shown in Figure 3, otherwise can affect be sprayed in cylinder 120 with the mixing of air.
In order to avoid the situation of above-mentioned interference, arranging described oil sprayer 101 length stretched in firing chamber 100 in the present embodiment is 5 ~ 10mm.
In addition, described oil sprayer 101 is 5 ~ 10 degree with the angle theta of described firing chamber 100 axial direction.If angle is excessive, then probably interfere between the oil bundle 101a of two oil sprayer 101 injections.
In the present embodiment, have employed two oil sprayers and be arranged symmetrically in top of combustion chamber, do not need the essential structure destroying existing in-cylinder direct injection combustion system.
In other embodiments, two described oil sprayers 101 also can be arranged at described spark plug 102 both sides asymmetrically, do not interfere as long as meet between the oil bundle 101a of oil sprayer 101 injection and spark plug 102, and do not interfere between the oil bundle 101a of two oil sprayer 101 injections.
In addition, in the present embodiment, oil sprayer 101 should be fixedly connected with cylinder head 130, can realize being connected by being formed at oil sprayer 101 and the screw thread in cylinder head 130 respectively, or otherwise connect, to ensure can not offset from each other between oil sprayer 101 and cylinder head 130.
In the present embodiment, described oil sprayer 101 is porous type oil sprayer.Concrete, the spray orifice of described oil sprayer 101 is 6 ~ 7, and the diameter of described spray orifice is 150 ~ 180 μm.Porous type oil sprayer is compared to oil sprayer of the prior art, spray particle diameter is little, affect little by back pressure in cylinder (pressure contrary with spraying flow direction be subject to of namely spraying), the form of spraying can be controlled preferably, and there is fast response time, stability is high and dredge oil amount is little advantage.
The model of oil sprayer 101 specifically can be selected according to the discharge capacity of motor, such as the supercharged direct-injection engine of discharge capacity 2.0L, if with the set-up mode of a prior art oil sprayer, need to select the static jet pressure down-off of 100bar to be the oil sprayer of 920g/min, the static jet pressure down-off of two 100bar then can be selected in the present embodiment to be the oil sprayer of 600 ~ 650g/min, namely the oil sprayer 101 that two flow coefficients are a little bit smaller is selected, like this when single oil sprayer 101 sprays, the flow coefficient of spraying is 65 ~ 70% of prior art, and when two oil sprayers 101 spray simultaneously, the total discharge coefficient of spraying can improve 30 ~ 40% than prior art, meanwhile, the oil mass being assigned to each oil sprayer 101 spray orifice during injection reduces nearly 40%, greatly can reduce the penetration degree of oil bundle 101a, reduces the amount of dilution of machine oil and the pre-ignition caused thereof and super detonation frequency.
As can be seen here, this combustion system can carry out the flow coefficient of adjustable spraying by the quantity controlling to carry out the oil sprayer 101 sprayed simultaneously.
With reference to Fig. 3 composition graphs 5, in the present embodiment, described piston 110 comprises to be arranged and coaxial bottom 113, first annular joint 111 and the second annular joint 112 connected successively along the direction towards top, described firing chamber 100;
Described first annular joint 111 has two ends in axial direction, and described second annular joint 112 has inner circumference edge 112a radially and outer periphery 112b;
One end of described first annular joint 111 is connected with the circumferential edge 113a of described bottom 113, and the other end is connected with the inner circumference edge 112a of described second annular joint 112;
The inner wall sealing contact of firing chamber 100 described in the outer periphery 112b of described second annular joint 112.
Further, the internal diameter of one end that described first annular joint 111 is connected with described bottom 113 is less than the internal diameter of the other end.
Further, described first annular joint 111 is convex in described cylinder 120 inwall.First annular joint 111 is curvilinear at the shape of cross section of axis.
As can be seen here, in the present embodiment, piston 110 is formed by connecting by the annular joint 111 in bottom 113, first and the second annular joint 112, the bottom surface of 113, bottom and the inwall of the first annular joint 111 are combined to form the end face of the shallow basin type structure of piston 110, as shown in Figure 4, make the bottom surface of firing chamber 100 more smooth, be therefore sprayed in cylinder 120 resistance be subject to when forming tumble motion less, be conducive to the Homogeneous phase mixing of spraying and air.
In the present embodiment, with reference to Fig. 3-4, in-cylinder direct injection combustion system also comprises the intake duct 103 and air outlet flue 104 that are connected with top, described firing chamber 100;
Described intake duct 103 and described air outlet flue 104 are arranged in outside the zone line of top, described firing chamber 100 cylinder head 130 respectively, and described intake duct 103 is positioned at the side of two oil sprayers 101, and described air outlet flue 104 is positioned at the opposite side of two oil sprayers 101.
Described intake duct 103 and described air outlet flue 104 all have two, and are arranged symmetrically with relative to described spark plug 102 respectively.
Here, adopt the Four valve structure of twin-inlet and double-exhaust passage, if motor is supercharged engine, then should suitably arrange larger by the Tumble and swirl of intake duct 103, such as, can be 1.5 ~ 3, to be conducive to the flowing of gas in cylinder 110; If motor is naturally aspirated engine, then the flow coefficient of intake duct 103 should suitably improve, such as, can be 1 ~ 1.5, have enough air inflows during to ensure large load operation; Accordingly, the flow coefficient of air outlet flue 104 should correspondingly improve, and should be greater than 0.7, discharges firing chamber 100 as soon as possible to make waste gas.
The advantage of above-mentioned layout is, under the operating mode of motor large load operation, twin-inlet can ensure enough air inflows, and because the Tumble and swirl of intake duct 103 is higher, air can be impelled in cylinder 120 to form strong large scale tumble motion, this tumble motion can help the mixing velocity of cylinder 120 internal spraying and air to accelerate on the one hand, on the other hand, the mixed gas that spraying and air are formed compression stroke top dead center due to the barrier effect being subject to bottom surface, firing chamber 100 can the turbulent flow of broken formation small scale, and then (turbulence intensity especially when lighting a fire in cylinder 120 can reach 35m can to improve turbulence intensity in cylinder 120
2/ s
2).Now, by Turbulent Flow Effects, after spark plug 102 is lighted a fire, flame has good velocity of propagation, forms good firing effect.
Introduce in the embodiment of the present invention fuel-injecting method when adopting above-mentioned in-cylinder direct injection combustion system below, wherein, described in-cylinder direct injection combustion system is electrically connected with control unit of engine (not shown), and set Optimal Load transition point, definition: when engine load operating mode is greater than this critical point of load, for high load working condition, when engine load operating mode is less than this critical point of load, for middle small load condition, then above-mentioned definition is input in control unit of engine, for defining jet mode;
In this fuel-injecting method:
Under the operating mode of motor large load operation, in the intake stroke, control two described oil sprayers 101 to spray simultaneously;
Under the operating mode that Smaller load runs within the engine, in the intake stroke, control an oil sprayer and spray, or, control two described oil sprayers 101 and spray in turn or interrupted injection.
Further, described combustion system also comprises and is positioned at cylinder and the bent axle (not shown) be connected to bottom described firing chamber 100;
Control described oil sprayer 101 to start when budc crank angle is 280 ~ 300 degree to spray.
Further, controlling the flow coefficient of described oil sprayer 101 when jet pressure is 100bar is 600 ~ 650g/min.
It should be noted that in the present embodiment, motor adopts Homogeneous phase mixing combustion engine, and under all operating modes, all adopt the pattern that Homogeneous phase mixing burns, the actual mixing ratio of oil inflame is close to chemically correct fuel.
In the present embodiment, the mode of operation that two oil sprayers 101 spray simultaneously is adopted when motor high load working condition runs, significantly discharge time can be shortened while the flow coefficient promoting spraying, such as originally needed 150 crank angles to complete injection, only need 90 crank angles just can complete now, so, in the process of air inlet, the fuel oil sprayed has the more time complete evaporation atomization and mix with air, is conducive to the uniformity improving mixed gas in cylinder 120 when spark plug 102 is lighted a fire;
The mode of operation that an oil sprayer sprays is adopted when little operating mode is run within the engine, or, (each oil sprayer sprays 1 time at every turn to adopt oil sprayer 101 to spray in turn, two oil sprayers are used alternatingly) or interrupted injection is (spray of each oil sprayer repeatedly, two oil sprayers are used alternatingly) mode of operation, namely the same time only has an oil sprayer 101 to spray, and reduces the flow coefficient of spraying; On the one hand, the flow coefficient of each oil sprayer 101 is only of the prior art 65 ~ 70%, can proper extension discharge time, and can adopt larger jet pressure, improves the working stability of needle-valve in oil sprayer 101; On the other hand, oil sprayer 101 is used alternatingly, and can reduce the time of needle-valve continuous operation in oil sprayer 101, extends the working life of oil sprayer 101.
To sum up, above-mentioned fuel-injecting method both can ensure the quality of spraying, flow coefficient requirements different under meeting again different operating mode.
Although the present invention discloses as above, the present invention is not defined in this.Any those skilled in the art, without departing from the spirit and scope of the present invention, all can make various changes or modifications, and therefore protection scope of the present invention should be as the criterion with claim limited range.
Claims (8)
1., for a fuel-injecting method for in-cylinder direct injection combustion system, described in-cylinder direct injection combustion system comprises firing chamber, and described top of combustion chamber is connected with spark plug and oil sprayer; It is characterized in that:
Described spark plug and described oil sprayer are all positioned at the zone line of top of combustion chamber;
Described oil sprayer has two, is symmetricly set in described spark plug both sides;
Do not interfere between the oil bundle that described oil sprayer sprays and described spark plug, and do not interfere between the oil bundle of two oil sprayer injections;
Under the operating mode of motor large load operation, in aspirating stroke, control two described oil sprayers and spray simultaneously;
Under the operating mode that Smaller load runs within the engine, in aspirating stroke, control two described oil sprayers and spray in turn or intermittently spray in turn.
2. fuel-injecting method as claimed in claim 1, it is characterized in that, under all operating modes of motor, the actual mixing ratio of oil inflame is close to chemically correct fuel.
3. fuel-injecting method as claimed in claim 1, it is characterized in that, the described oil sprayer length stretched in firing chamber is 5 ~ 10mm.
4. fuel-injecting method as claimed in claim 3, it is characterized in that, the angle of described oil sprayer and described firing chamber axial direction is 5 ~ 10 degree.
5. fuel-injecting method as claimed in claim 1, it is characterized in that, described oil sprayer is porous type oil sprayer.
6. fuel-injecting method as claimed in claim 5, it is characterized in that, the spray orifice of described oil sprayer is 6 ~ 7, and the diameter of described spray orifice is 150 ~ 180 μm.
7. fuel-injecting method as claimed in claim 1, it is characterized in that, described in-cylinder direct injection combustion system also comprises the intake duct and air outlet flue that are connected with described top of combustion chamber;
Described intake duct and described air outlet flue are arranged in outside the zone line of described top of combustion chamber respectively, and described intake duct is positioned at the side of two oil sprayers, and described air outlet flue is positioned at the opposite side of two oil sprayers.
8. fuel-injecting method as claimed in claim 7, it is characterized in that, described intake duct and described air outlet flue all have two, and are arranged symmetrically with relative to described spark plug respectively.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410268140.7A CN105317573B (en) | 2014-06-16 | 2014-06-16 | Fuel-injecting method for in-cylinder direct-jet combustion system |
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| CN201410268140.7A CN105317573B (en) | 2014-06-16 | 2014-06-16 | Fuel-injecting method for in-cylinder direct-jet combustion system |
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| CN105317573B CN105317573B (en) | 2018-03-30 |
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| CN110821665A (en) * | 2018-08-07 | 2020-02-21 | 大连理工大学 | Dual-fuel plasma nozzle type two-stroke engine based on reformed gas and combustion control method |
| CN110821660A (en) * | 2018-08-07 | 2020-02-21 | 大连理工大学 | Reformed gas-based single-fuel spark plug type four-stroke engine and combustion control method |
| CN110821650A (en) * | 2018-08-07 | 2020-02-21 | 大连理工大学 | Dual-fuel ignition chamber type two-stroke engine and combustion control method |
| CN110821666A (en) * | 2018-08-07 | 2020-02-21 | 大连理工大学 | Dual-fuel spark plug type four-stroke engine and combustion control method |
| CN110821659A (en) * | 2018-08-07 | 2020-02-21 | 大连理工大学 | Reformed gas-based single-fuel ignition chamber type two-stroke engine and combustion control method |
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| CN110821654A (en) * | 2018-08-07 | 2020-02-21 | 大连理工大学 | Dual-fuel spark plug type four-stroke engine based on reformed gas and combustion control method |
| CN110821653A (en) * | 2018-08-07 | 2020-02-21 | 大连理工大学 | Dual-fuel ignition chamber type four-stroke engine based on reformed gas and combustion control method |
| CN110821661B (en) * | 2018-08-07 | 2022-04-01 | 大连理工大学 | Dual-fuel compression-ignition four-stroke engine based on reformed gas and combustion control method |
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