CN104806382A - Fuel conveying method for internal combustion engine using gas-liquid two-phase natural gas as fuel - Google Patents
Fuel conveying method for internal combustion engine using gas-liquid two-phase natural gas as fuel Download PDFInfo
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- CN104806382A CN104806382A CN201510153562.4A CN201510153562A CN104806382A CN 104806382 A CN104806382 A CN 104806382A CN 201510153562 A CN201510153562 A CN 201510153562A CN 104806382 A CN104806382 A CN 104806382A
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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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- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
The invention discloses a fuel conveying method for an internal combustion engine using a gas-liquid two-phase natural gas as the fuel. The method comprises the following steps: conveying a liquid-state compressed natural gas source and a gas-state compressed natural gas source to a heat insulation common rail in a heat insulation manner; mixing the liquid-state compressed natural gas source with the gas-state compressed natural gas source in the thermal insulation common rail, and conveying the mixture into a gas cylinder through an electrically controlled fuel injector; the fuel entering the heat insulation common rail (5) is divided into a liquid route and a gas route; the liquid route is conveyed to the heat insulation common rail (5) by a liquid-state compressed natural gas cylinder (1) through a heat insulation low-pressure pipe (2) and a heat insulation pressure pump (10); and the gas route enters the heat insulation common rail (5) by a gas-state compressed natural gas cylinder (7) through corresponding pipes and valves. The fuel conveying method for the internal combustion engine using the gas-liquid two-phase natural gas as the fuel allows the gas phase natural gas and the liquid phase natural gas to be flashed and boiled upon entering the gas cylinder; and real-time designs and controls of the gas and liquid components of the two-phase natural gas are subjected to different working conditions. Due to the fact that the gas-liquid two-phase natural gas is combusted, the CO emission, the CO2 emission and the PM emission are substantially low, without NMHC. The fuel is injected during the compression process, and accordingly the HC emission is low. The temperature in the cylinder is low; the NOX emission is low; and the emission performance is low.
Description
Affiliated field
The present invention relates to a kind of I. C engine combustion system structure, particularly relate to the combustion system using rock gas as fuel.
Background technique
In current natural gas internal-combustion engine, be no matter the central port injection adopting intake manifold place, the multi-point injection at intake manifold place or the inner cylinder direct injection be contained in by blast nozzle on cylinder cap, its fuel sprayed is all gaseous natural gas.In non-direct-jet natural gas machine, the mixed gas of rock gas and air reduces by 12% compared to the heat vale of mixture of diesel oil and air; Meanwhile, rock gas enters in cylinder with gaseous state, occupy certain volume of cylinder, makes air inlet amount than when using liquid fuel and reduces about 10%.In-cylinder direct-jet natural gas internal-combustion engine is that rock gas enters cylinder at the end of aspirating stroke, though can increase air inflow like this, rock gas mixed gas is relative to liquid fuel mixed gas, and fuel can not absorb vaporization heat by carburation by evaporation, and intake temperature also can not be made to reduce.So the intake temperature of current natural gas motor is higher, the heat load of combustion chamber component is higher, and NO
xbe when high-temperature oxygen-enriched, have a large amount of generation, therefore be unfavorable for improving reliability and reducing discharge.
Summary of the invention
In view of the above deficiency of prior art, the object of the invention is to the I. C engine combustion system proposing a kind of gas-liquid two-phase rock gas, use that the discharge of the internal-combustion engine of this system is low, reliability is high.
The object of the invention is by following technological means realize.
Adopt gas-liquid two-phase rock gas to be the motor fuel delivery method of fuel, liquid compressed natural gas source and gaseous state compressed natural gas source are delivered to an adiabatic common rail by thermal insulation, complete mixing in adiabatic common rail after, are delivered to cylinder through an electric-controlled fuel injector; Its concrete course of conveying and operating conditions are:
1) fuel entering adiabatic common rail 5 has fluid path and gas circuit two-way: fluid path is delivered to adiabatic common rail 5 by liquid compressed natural gas bottle (1) by adiabatic low-voltage tube 2 and adiabatic pressure pump 10; Gas circuit enters adiabatic common rail 5 by gaseous compressed natural gas cylinder 7 by corresponding pipe valve;
2) to be exported by adiabatic common rail 5 through the mixed fuel of adiabatic common rail 5 be delivered to cylinder after electric-controlled fuel injector 8;
3) described fluid path and gas circuit arrange corresponding pipe valve and are connected, and arrange corresponding pressure transducer in gas circuit; Internal combustion engine electronic-control unit 9
Adiabatic low-voltage tube 2 is connected with adiabatic pressure pump 10 import; Adiabatic pressure pump 10 is connected with adiabatic common rail 5 after solenoid valve 4 by adiabatic high-voltage tube; Adiabatic common rail 5 is connected with the electric-controlled fuel injector 8 on cylinder by adiabatic high-voltage tube; Gaseous compressed natural gas cylinder 7 is connected with adiabatic common rail 5 by adiabatic high-voltage tube; Adiabatic pressure pump 10, solenoid valve 4, adiabatic common rail 5, pressure transducer 6 and electric-controlled fuel injector 8 are all electrically connected with internal combustion engine electronic-control unit 9 and control adiabatic pressure pump 10, solenoid valve 4, adiabatic common rail 5, pressure transducer 6 and electric-controlled fuel injector 8 and control with the optimal combustion condition meeting internal-combustion engine.
Adopt technological scheme as above, its running is:
The liquified natural gas be stored in gas cylinder is delivered in adiabatic pressure pump by heat-insulated pipe, liquified natural gas is forced into about 20MPa and delivers in adiabatic common rail by adiabatic high-voltage tube and solenoid valve by pressure pump, being stored in pressure is that gaseous compressed rock gas in 20MPa gas cylinder is delivered in adiabatic common rail by heat-insulated pipe, by the opening/closing time of Controlling solenoid valve and then deliver to electric-controlled fuel injector after carrying out gas-liquid two-phase real-time design to the rock gas in common rail.Gas-liquid two-phase rock gas sprays in compression process, and passes through spark ignition.
When two phase flow rock gas sprays to low-voltage high-temperature environment, the degree of superheat of gas increases, and gas expands, form foam and grow up, sharply disengage at nozzle exit gas, overcome the viscous force of liquid and surface tension and gas explosion atomization occurs, and producing violent flash distillation boiling phenomenon; In addition, the temperature gradient entered in cylinder due to two-phase rock gas is large, and heat absorption evaporation is fast; Two phase flow rock gas and air is finally made to be easy to generate homogeneous mixture.
At normal temperatures, when pressure is changed to 0 ~ 50MPa, the compressibility coefficient β of diesel oil (C10 ~ C21 hydrocarbon) is (4 ~ 6.5) × 10
-4(MPa)
-1, and be greater than the compressibility coefficient of weight values oil, if LNG Liquefied natural gas (CH because of the compressibility coefficient of light oil
4) compressibility coefficient be 5 × 10
-3(MPa)
-1, giving 1m
3lNG Liquefied natural gas constant entropy be pressurized to 20MPa after, compression volume ratio is:
ΔV/V＝β·p (1)
The absorption merit of compressed natural gas is:
W＝PV (2)
Because of in constant entropy situation, this absorption merit is all converted into heat Q, does not wherein consider the change of specific heat capacity after liquefied natural gas vaporization,
W＝Q＝c·m·Δt (3)
Data are brought into above-mentioned formula to obtain: after LNG Liquefied natural gas constant entropy is pressurized to 20MPa, temperature rising 7.577K.According to the saturation temperature of LNG Liquefied natural gas, rock gas is now still liquid.
In the structure of this combustion system, because Austenitic Stainless Steel has excellent cryogenic property, therefore in heat-insulated pipe, high pressure oil pump, contact the Austenitic Stainless Steel of LNG part, adiabatic rail employing 304L/316 material.The cold insulation of heat-insulated pipe, adiabatic rail adopts cladded type adiabatic, its thermoinsulation material adopts the deep cooling having obtained successful Application in production practices to improve urethane foam (PUH, PUB), but the cold insulation contacting LNG part in high pressure oil pump adopts surface spraying pottery to solve.
The real-time design of fuel controls existing large quantity research at present, and the real-time design of gas-liquid two-phase rock gas controls also to can refer to carry out.
Following table is that rock gas compares with the physico-chemical property of gasoline, diesel oil:
The physico-chemical property of table 1 rock gas and gasoline, diesel oil
| Physico-chemical property | Rock gas | Gasoline | Diesel oil |
| Molecular formula | Main component CH <sub>4</sub> | C5 ~ C12 hydrocarbon | C10 ~ C21 hydrocarbon |
| Boiling point/DEG C | -162 | 125.7 | 180～360 |
| Octane value (RON) | 130 | 70～97 | 20～30 |
| Cetane number | Low | -15 | 40～55 |
| Spontaneous ignition temperature/DEG C | 650 | 420 | ≈250 |
| Stoichiometric air-fuel ratio | 16.4 | 14.8～15.1 | 14.3 |
| Lower calorific value/MJkg <sup>-1</sup> | 50.00 | 43.97 | 42.50～44.40 |
| Vaporization heat/kJkg <sup>-1</sup> | 297 | 250 | |
| Velocity of propagation of flame/cms <sup>-1</sup> | 34～37 | 35～47 | |
| Density/kgm <sup>-3</sup> | 430 | 679 | 860 |
| Viscosity/mm2s <sup>-1</sup> | 0.28～0.59(20℃) | 3～8 |
Can find out, the H/C of rock gas is than large, therefore calorific value is high.Enter cylinder and be low temperature two-phase-flow and rock gas octane value is high, so compression ratio can bring up to desirable about 15, make increase compression ratio obtain compromise to the Beneficial Effect of the thermal efficiency and the mechanical loss of increase; The raising of compression ratio equally also can improve cold-start performance.
Liquified natural gas vaporization needs to absorb a large amount of heat, and the rock gas after vaporization is five atomic gas, has very high specific heat capacity, and when 1000K, the specific heat at constant pressure of gaseous natural gas is 2.2 times of air, is CO
21.3 times, therefore just need to absorb more heat to heat up.Finally make burning finishing temperature lower, heat transfer loss is few, improves the thermal efficiency equally.
Because a large amount of H burning becomes harmless H
2o, liquified natural gas is impure few in addition, contained CH
4purity can reach more than 99%, so CO, CO of discharging after burning
2, unburned hydrocarbons and the harmful matter such as soot, particulate reduce.At NO
xdischarge aspect, because burning finishing temperature is lower, rock gas can substitute CO before combustion completely
2eGR effect, make NO
xdischarge lower.But mixed gas velocity of propagation of flame is slow, after-burning is serious, thus causes NO
xthe pyroreaction time long, the raising of compression ratio can make maximum combustion temperature increase, and which adds NO
xdischarge.But there is lower NO than current natural gas engine
xdischarge.
Compared to gasoline and diesel oil, the cetane number of rock gas is very low, and spontaneous ignition temperature is high, therefore burning is slower.When equal in quality, natural gas, because H will consume many many oxygen, so the stoichiometric air-fuel ratio of rock gas is large.Though the density of liquified natural gas is less than petrol and diesel oil, volume energy density is that the twice of compressed natural gas is many.
The main consideration of adiabatic low-voltage tube is insulation, makes liquified natural gas in flow process, be unlikely to vaporization.Adiabatic high-voltage tube still will consider insulation, the impact separately because there being gas-liquid two-phase flow also should consider cavitation pitting in adiabatic high-voltage tube.If because strong pressure wave passes to bubble place or bubble is transported to high pressure position, then bubble instantaneously can reduce, collapses and produce high hydraulic shock power, cause noise and vibration, pressure surge repeated action, when adiabatic high-voltage tube wall, also can make its reliability decrease.
Because needing charge oil pressure not change with the change of the operation point of motor, adopt ram type pump for this reason.But plunger coupled parts itself must use surface treatment, except considering sealing, also require thermal insulation, require that adiabatic Another reason is under cryogenic, plunger coupled parts has low temperature brittleness.In compressed liquid rock gas process, keep away the leakage between unavoidable plunger and plunger bushing, the gas-liquid two-phase flow of leakage all can become gas in adiabatic high-pressure service pump, and the natural of gaseous state can be reclaimed by charcoal tank.Because the pressure pulsation of simplex pump is large, and will ensure that the gas-liquid two-phase flow by heating does not reflux, therefore adiabatic high-pressure service pump adopts multi-cylinder axial plunger fuel pump.The increase of jet pressure, spray can be thicker, and the quantity that jet velocity increase makes power be atomized grain group also increases, and Sauter mean value reduces.But considered flash distillation boiling phenomenon, liquified natural gas vapourizing temperature gradient is large, liquified natural gas temperature when compressing raises and is unlikely to too many, and the pressure of compressed natural gas cylinder is not higher than 20MPa, therefore gas-liquid two-phase flowing pressure is decided to be about 20MPa.
Adiabatic common rail must be incubated and also will consider the impact of air pocket.Adiabatic rail is wanted outside setting pressure sensor.To know the vaporization situation in adiabatic common rail, for the determination of the two phase flow of real-time design control provides basic data.
Adopt basic scheme of the present invention, also can be optimized from different perspectives in actual implementation process, such as:
After motor adopts exhaust gas turbocharge, its power character, Economy and emission performance are significantly improved.Consider technology maturation, therefore adopt single-stage exhaust gas bypass turbosupercharger.
Adopt VVT to reduce pumping loss, make up the deficiency that average mixing direct-injection system can not reduce pumping loss.
Commercial direct injection gasoline engine mostly utilizes straight air flue to produce and rolls stream, but depends on the integrated application of the technology such as oil supply system, control system and combustion system, has designed and developed larger difficulty.And this combustion system have employed helical intake with the combustion recess shape at fitting piston top.The eddy current produced can make to be sprayed at compression process and still keep being atomized mixing faster latter half.This mixed Daqu mode combines feature that is spray-guided and air-flow guiding, one is spray relatively near spark plug and directly do not extend into spark plug place, doing so avoids two-phase rock gas adhesional wetting spark plug and cause spark plug to catch fire and carbon distribution, two is make full use of eddy current turning effort to accelerate spray evaporation.
Spray in compression process, form homogeneous mixture rapidly.Wish that the reason of carrying out spraying in the time late is as far as possible the HC discharge reduced because gap effect causes.If the time of mixed Daqu can be postponed as far as possible, near the crack in compression process between piston and cylinder sleeve, mostly be pure air.Be pressed in compression process in crack and should not contain rock gas, thus reduce HC discharge, improve the thermal efficiency.
At guarantee NO
xstrengthen ignition advance angle when less as far as possible.Make engine operation at detonation edge, thus obtain good power character and Economy.
Compared with prior art, the invention has the beneficial effects as follows:
This combustion system adopts and uses gas-liquid two-phase rock gas, and it has following advantage compared with current natural gas engine, diesel engine and petrol engine:
(1) because using the scheme such as in-cylinder direct injection, high compression ratio, therefore there is high power character and Economy;
(2) because of burning is gas-liquid two-phase rock gas, therefore CO, CO
2, PM discharge low, without NMHC; Employing compression process is sprayed, and HC discharge is low; Cylinder temperature is low, NO
xdischarge low; Therefore there is extremely low emission performance;
(3) combustion temperature is low, and heat load is light, therefore in cylinder, part reliability is high.
Accompanying drawing explanation
Fig. 1 is the I. C engine combustion system essential structure schematic diagram of gas-liquid two-phase rock gas.
Fig. 2 is that schematic diagram arranged by nozzle and spark plug.
Fig. 3 is firing chamber schematic diagram.
Embodiment
Below in conjunction with accompanying drawing, the technology of the present invention content is described in further detail.
As shown in Figure 1, the gas-liquid two-phase rock gas I. C engine combustion system of the embodiment of the present invention, its composition is: the fuel entering adiabatic common rail 5 has fluid path and gas circuit two-way: fluid path is delivered to adiabatic common rail 5 by liquid compressed natural gas bottle 1 by adiabatic low-voltage tube 2 and adiabatic pressure pump 10; Gas circuit enters adiabatic common rail 5 by gaseous compressed natural gas cylinder 7 by corresponding pipe valve;
2) to be exported by adiabatic common rail 5 through the mixed fuel of adiabatic common rail 5 be delivered to cylinder after electric-controlled fuel injector 8;
3) described fluid path and gas circuit arrange corresponding pipe valve and are connected, and arrange corresponding pressure transducer in gas circuit; Internal combustion engine electronic-control unit 9
Low-voltage tube 2 is connected with adiabatic pressure pump 10 import; Adiabatic pressure pump 10 is connected with adiabatic common rail 5 after solenoid valve 4 by adiabatic high-voltage tube; Adiabatic common rail 5 is connected with the electric-controlled fuel injector 8 on cylinder by adiabatic high-voltage tube 3; Gaseous compressed natural gas cylinder 7 is connected with adiabatic common rail 5 by adiabatic high-voltage tube; Adiabatic pressure pump 10, solenoid valve 4, adiabatic common rail 5, pressure transducer 6 and electric-controlled fuel injector 8 are all electrically connected with internal combustion engine electronic-control unit 9 and control adiabatic pressure pump 10, solenoid valve 4, adiabatic common rail 5, pressure transducer 6 and electric-controlled fuel injector 8 and control with the optimal combustion condition meeting internal-combustion engine.Internal combustion engine electronic-control unit 9 carries out the control of gas-liquid two-phase real-time traffic to the liquified natural gas and gaseous natural gas that enter adiabatic common rail 5.
Spark plug arranges that Fig. 2 is shown in by schematic diagram.For identical ignition voltage requirement, surface gap spark can skip more large electrode gap than air clearance spark, like this, can form larger flame kernel, and fire behaviour is obviously improved in catching fire subsequently.Because this combustion system is low-temperature burning, the spark-discharge gap stretching into firing chamber is deeper of value to catching fire of mixed gas.Therefore adopt the surface gap type spark plug that calorific value is less.
This combustion system adopts ω firing chamber with the level as shown in Figure 3.Make intake swirl be maintained in piston head pit near, be also coordinate multiport nozzle simultaneously.The object of step is had to be squeeze stream to utilize and promote two-phase rock gas and air mixing and burning against squeezing stream, very favourable to improving combustion and emission.
Claims (2)
1. employing gas-liquid two-phase rock gas is the motor fuel delivery method of fuel, it is characterized in that, liquid compressed natural gas source and gaseous state compressed natural gas source are delivered to an adiabatic common rail by thermal insulation, complete mixing in adiabatic common rail after, are delivered to cylinder through an electric-controlled fuel injector; Its concrete course of conveying and operating conditions are:
1) fuel entering adiabatic common rail (5) has fluid path and gas circuit two-way: fluid path is delivered to adiabatic common rail (5) by liquid compressed natural gas bottle (1) by adiabatic low-voltage tube (2) and adiabatic pressure pump (10); Gas circuit enters adiabatic common rail (5) by gaseous compressed natural gas cylinder (7) by corresponding pipe valve;
2) after electric-controlled fuel injector (8), cylinder is delivered to by adiabatic common rail outlet through the mixed fuel of adiabatic common rail;
3) described fluid path and gas circuit arrange corresponding pipe valve and are connected, and arrange corresponding pressure transducer in gas circuit; Internal combustion engine electronic-control unit (9);
Adiabatic low-voltage tube (2) is connected with adiabatic pressure pump (10) import; Adiabatic pressure pump (10) is connected with adiabatic common rail after solenoid valve (4) by adiabatic high-voltage tube; Adiabatic common rail is connected with the electric-controlled fuel injector on cylinder by adiabatic high-voltage tube; Gaseous compressed natural gas cylinder (7) is connected with adiabatic common rail by adiabatic high-voltage tube; Adiabatic pressure pump (10), solenoid valve (4), adiabatic common rail (5), pressure transducer (6) and electric-controlled fuel injector (8) are all electrically connected with internal combustion engine electronic-control unit (9) and control adiabatic pressure pump (10), solenoid valve (4), adiabatic common rail (5), pressure transducer (6) and electric-controlled fuel injector (8) and control with the optimal combustion condition meeting internal-combustion engine.
2. gas-liquid two-phase rock gas I. C engine combustion system according to claim 1, it is characterized in that, internal combustion engine electronic-control unit (9) carries out the control of gas-liquid two-phase real-time traffic to the liquified natural gas and gaseous natural gas that enter adiabatic common rail (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510153562.4A CN104806382B (en) | 2015-04-02 | 2015-04-02 | It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510153562.4A CN104806382B (en) | 2015-04-02 | 2015-04-02 | It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104806382A true CN104806382A (en) | 2015-07-29 |
| CN104806382B CN104806382B (en) | 2017-06-13 |
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ID=53691517
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510153562.4A Expired - Fee Related CN104806382B (en) | 2015-04-02 | 2015-04-02 | It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114810447A (en) * | 2022-04-11 | 2022-07-29 | 哈尔滨工程大学 | Device and method for testing gas-liquid two-phase ratio in transient injection process of ammonia fuel with phase change |
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|---|---|---|---|---|
| JP2004150333A (en) * | 2002-10-30 | 2004-05-27 | Aisan Ind Co Ltd | Fuel supply device of liquefied gas internal combustion engine |
| CN103069137A (en) * | 2010-06-07 | 2013-04-24 | 阿尔塞特知识产权公司 | Bi-fuel engine with variable air fuel ratio |
| CN103422999A (en) * | 2012-05-17 | 2013-12-04 | 卡特彼勒公司 | Direct injection gas engine and method |
| CN103573452A (en) * | 2012-08-08 | 2014-02-12 | 卡特彼勒公司 | Dual fuel engine and evaporated natural gas system |
| CN103958860A (en) * | 2011-11-30 | 2014-07-30 | 爱三工业株式会社 | Fuel supply control apparatus for bi-fuel internal combustion engine, and method of switching fuel in bi-fuel internal combustion engine |
-
2015
- 2015-04-02 CN CN201510153562.4A patent/CN104806382B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004150333A (en) * | 2002-10-30 | 2004-05-27 | Aisan Ind Co Ltd | Fuel supply device of liquefied gas internal combustion engine |
| CN103069137A (en) * | 2010-06-07 | 2013-04-24 | 阿尔塞特知识产权公司 | Bi-fuel engine with variable air fuel ratio |
| CN103958860A (en) * | 2011-11-30 | 2014-07-30 | 爱三工业株式会社 | Fuel supply control apparatus for bi-fuel internal combustion engine, and method of switching fuel in bi-fuel internal combustion engine |
| CN103422999A (en) * | 2012-05-17 | 2013-12-04 | 卡特彼勒公司 | Direct injection gas engine and method |
| CN103573452A (en) * | 2012-08-08 | 2014-02-12 | 卡特彼勒公司 | Dual fuel engine and evaporated natural gas system |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114810447A (en) * | 2022-04-11 | 2022-07-29 | 哈尔滨工程大学 | Device and method for testing gas-liquid two-phase ratio in transient injection process of ammonia fuel with phase change |
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