CN110953066B - Engine and in-cylinder split-layer combustion method - Google Patents
Engine and in-cylinder split-layer combustion method Download PDFInfo
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- CN110953066B CN110953066B CN201811126324.4A CN201811126324A CN110953066B CN 110953066 B CN110953066 B CN 110953066B CN 201811126324 A CN201811126324 A CN 201811126324A CN 110953066 B CN110953066 B CN 110953066B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/12—Other methods of operation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/242—Arrangement of spark plugs or injectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4285—Shape or arrangement of intake or exhaust channels in cylinder heads of both intake and exhaust channel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/01—Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/104—Intake manifolds
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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
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
The utility model provides an engine, includes cylinder, cylinder cap, piston and sprayer, and the cylinder cap setting is on the cylinder, and piston movably sets up in the cylinder, forms the combustion chamber between cylinder cap and the piston, and the sprayer setting is on the cylinder cap, and the sprayer is used for spouting into fuel to the combustion chamber, is equipped with spiral intake duct and exhaust passage on the cylinder cap, is connected with the exhaust gas guide way between spiral intake duct and the exhaust passage, is equipped with the exhaust gas control valve of control exhaust gas flow on the exhaust gas guide way, when the engine was when the intake stroke, makes waste gas and air form the combustion chamber that the vortex gas mixture got into the cylinder behind the spiral intake duct. The engine can avoid the detonation caused by the self-ignition of the mixed gas at the tail end of the gasoline fuel under the condition of high compression ratio, and improve the heat efficiency. The invention also relates to a method for in-cylinder split-layer combustion of a fuel.
Description
Technical Field
The invention relates to the technical field of compression ignition of engines, in particular to an engine and a fuel cylinder internal division compression ignition method.
Background
The existing ignition type gasoline engine is limited by knocking, and the compression ratio is far lower than that of a diesel engine mainly based on compression ignition. The thermal efficiency of existing gasoline engines is relatively low, since the thermal efficiency of the engine is directly related to the compression ratio.
At present, the gasoline engine mainly adopts tumble stratification, and because tumble is easy to break and poor in retentivity in the compression process, stratified mixed gas formed in an intake stroke cannot be always kept before ignition, stable and proper oil-gas mixed gas is difficult to form near a spark plug, and the stratified advantage is not favorable for being played.
Disclosure of Invention
In view of this, the present invention provides an engine, which can avoid knocking caused by spontaneous combustion of a mixed gas at a gasoline fuel end under a high compression ratio condition, and improve thermal efficiency.
The utility model provides an engine, includes cylinder, cylinder cap, piston and sprayer, and the cylinder cap setting is on the cylinder, and piston movably sets up in the cylinder, forms the combustion chamber between cylinder cap and the piston, and the sprayer setting is on the cylinder cap, and the sprayer is used for spouting into fuel to the combustion chamber, is equipped with spiral intake duct and exhaust passage on the cylinder cap, is connected with the exhaust gas guide way between spiral intake duct and the exhaust passage, is equipped with the exhaust gas control valve of control exhaust gas flow on the exhaust gas guide way, when the engine was when the intake stroke, makes waste gas and air form the combustion chamber that the vortex gas mixture got into the cylinder behind the spiral intake duct.
In an embodiment of the invention, the end surface of the piston is located in the combustion chamber, said end surface being recessed away from the cylinder head.
In an embodiment of the present invention, an end surface of the piston is recessed towards a direction away from the cylinder head to form a first combustion groove and a second combustion groove, the first combustion groove is located in the middle of the piston, and the second combustion groove is arranged along the circumferential direction of the first combustion groove.
In an embodiment of the invention, the fuel injector is arranged in the middle of the cylinder cover along the axis of the cylinder.
In the embodiment of the invention, a first inlet valve is arranged in the spiral inlet channel, a tangential inlet channel is also arranged on the cylinder cover, a second inlet valve is arranged in the tangential inlet channel, and an exhaust valve is arranged in the exhaust channel.
In an embodiment of the invention, a glow plug is further arranged on the cylinder cover, and the glow plug is arranged close to the fuel injector.
In the embodiment of the invention, an injection pipe is arranged at the end part of the exhaust gas guide passage, the injection pipe is arranged in the spiral air inlet passage, and the injection pipe is arranged along the air inlet direction of the spiral air inlet passage.
The present invention also provides a method for in-cylinder split-layer combustion of fuel using the engine described above, comprising the steps of:
during the intake stroke of the engine, exhaust gas and air form vortex mixed gas after passing through the spiral air inlet channel, the mixed gas enters the cylinder, and the exhaust gas and part of the air are thrown into the peripheral area close to the wall of the cylinder by the mixed gas under the action of vortex inertia;
fuel is sprayed into the cylinder by a fuel injector during an intake stroke, and the fuel is mixed with the waste gas and the air in the peripheral area under the action of vortex inertia after being gasified;
injecting fuel into the cylinder by using the fuel injector during a compression stroke, and mixing the gasified fuel with air in the central area of the cylinder; and
at the end of the compression stroke, the mixture in the central area is firstly compressed to form a plurality of fire nuclei, and the fire nuclei ignite the mixture in the peripheral area.
In an embodiment of the invention, the fuel is confined to the central region of the cylinder by a first combustion groove in the end face of the piston when the engine is in the compression stroke.
In the embodiment of the invention, when the engine is in a cold-start low-temperature working condition, the working medium in the cylinder is preheated by the preheating plug.
In the embodiment of the invention, when the engine is in a low-speed and low-load condition, the opening degree of the exhaust gas control valve is controlled to be smaller than 1/3 when the exhaust gas control valve is fully opened, and the injector is controlled to inject fuel in a single injection at the time of an intake stroke.
In the embodiment of the invention, when the engine is in a low-speed and large-load condition, the opening degree of the exhaust gas control valve is controlled to be smaller than 1/2 when the exhaust gas control valve is fully opened, and the injector is controlled to inject fuel for a plurality of times during the intake stroke.
In the embodiment of the invention, when the engine is in a medium-speed and low-load condition, the opening degree of the exhaust gas control valve is controlled to be greater than 1/2 when the exhaust gas control valve is fully opened, and the injector is controlled to inject fuel in a single injection at the time of an intake stroke.
In the embodiment of the invention, when the engine is in a medium-speed and large-load condition, the opening degree of the exhaust gas control valve is controlled to be smaller than 1/2 when the exhaust gas control valve is fully opened, and the injector is controlled to inject fuel a plurality of times during the intake stroke.
The cylinder cover of the engine is arranged on the cylinder, the piston is movably arranged in the cylinder, a combustion chamber is formed between the cylinder cover and the piston, the oil sprayer is arranged on the cylinder cover and is used for spraying fuel into the combustion chamber, the cylinder cover is provided with a spiral air inlet channel and an exhaust channel, an exhaust guide channel is connected between the spiral air inlet channel and the exhaust channel, an exhaust control valve for controlling the flow of exhaust gas is arranged on the exhaust guide channel, and when the engine is in an air inlet stroke, the exhaust gas and air form vortex mixed gas after passing through the spiral air inlet channel and enter the combustion chamber of the cylinder. The engine can avoid strong knock caused by self-ignition of mixed gas at the tail end of the gasoline fuel under the condition of high compression ratio under the condition of not changing the conventional gasoline fuel. Moreover, a higher compression ratio is significantly advantageous in terms of improvement in thermal efficiency. In addition, the control mode of gasoline stratified compression ignition provides a technical approach for controlling the non-equivalence ratio combustion processes such as gasoline lean combustion and the like.
Drawings
Fig. 1 is a partial structural schematic diagram of an engine of the present invention.
Fig. 2 is a schematic view of the structure of the engine of the present invention at the time of the intake stroke.
Fig. 3 is a schematic view of the engine of the present invention in a compression stroke.
FIG. 4 is a schematic flow diagram of the in-cylinder layered combustion method of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be further described with reference to the accompanying drawings.
Fig. 1 is a partial structural schematic diagram of an engine of the present invention. As shown in fig. 1, the engine 10 includes a plurality of sets of cylinders 11, a cylinder head 12, pistons 13, and injectors 14. The engine 10 is a gasoline engine, and the compression ratio of the engine 10 is 13-17, which is higher than that of the existing gasoline engine.
The end of the cylinder 11 is closed, and the head 12 is disposed on the open end of the cylinder 11.
The cylinder head 12 is provided with a helical inlet channel 121, a tangential inlet channel (not shown) and an outlet channel 123. The spiral air inlet channel 121, the tangential air inlet channel and the air outlet channel 123 are communicated with the combustion chamber 101, a first air inlet valve 122 for controlling the spiral air inlet channel 121 to be communicated with or disconnected from the combustion chamber 101 is arranged in the spiral air inlet channel 121, a second air inlet valve for controlling the tangential air inlet channel to be communicated with or disconnected from the combustion chamber 101 is arranged in the tangential air inlet channel, an air outlet valve 124 for controlling the air outlet channel 123 to be communicated with or disconnected from the combustion chamber 101 is arranged in the air outlet channel 123, and the functions and effects of the first air inlet valve 122, the second air inlet valve and the air outlet. An exhaust guide channel 125 is connected between the spiral inlet channel 121 and the outlet channel 123, that is, one end of the exhaust guide channel 125 is communicated with the spiral inlet channel 121, the other end of the exhaust guide channel 125 is communicated with the outlet channel 123, and the exhaust guide channel 125 is used for guiding part of the exhaust in the outlet channel 123 into the spiral inlet channel 121. The exhaust gas guide duct 125 is provided with an exhaust gas control valve 126 for controlling the flow rate of the exhaust gas, and the flow rate of the exhaust gas entering the helical intake duct 121 is controlled by adjusting the opening degree of the exhaust gas control valve 126. In the present embodiment, when the engine 10 is in the intake stroke, the opening degree of the exhaust gas control valve 126 is adjusted so that the exhaust gas enters the helical intake passage 121, and the exhaust gas and the air form a swirl mixture after passing through the helical intake passage 121 and enter the cylinder 11.
In another preferred embodiment, an end of the exhaust gas guiding passage 125 is provided with a jet pipe (not shown), the jet pipe is disposed in the spiral inlet 121, and the jet pipe is disposed along an air inlet direction of the spiral inlet 121. The ejector pipe introduces the waste gas into one side of the spiral air inlet channel 121, so that the layering degree of the waste gas and the air is increased, and the subsequent combustion can be carried out smoothly.
The piston 13 is movably arranged in the cylinder 11, the piston 13 is connected with a connecting rod through a pin shaft, the connecting rod is connected with a crankshaft, when the crankshaft rotates, the piston 13 reciprocates in the cylinder 11, and a combustion chamber 101 with variable volume is formed between the cylinder cover 12 and the piston 13. The end face 131 of the piston 13 is located in the combustion chamber 101, the end face 131 of the piston 13 is recessed in a direction away from the cylinder head 12, so that the recessed end face 131 of the piston 13 can be used as a small combustion chamber, and preferably, the end face 131 of the piston 13 is recessed in a direction away from the cylinder head 12 to form a first combustion groove 102 and a second combustion groove 103, the first combustion groove 102 is located in the middle of the piston 13, the axis of the first combustion groove 102 coincides with the axis of the piston 13, and the second combustion groove 103 is arranged along the circumferential direction of the first combustion groove 102, that is, the second combustion groove 103 is an annular groove. It is worth mentioning that the combustion chamber 101 of the cylinder 11 comprises a central zone 101a close to the axis of the cylinder 11 and a peripheral zone 101b close to the wall of the cylinder 11, i.e. the peripheral zone 101b surrounds the central zone 101a, wherein the first combustion groove 102 is located in the central zone 101a of the combustion chamber 101 and the second combustion groove 103 is located in the peripheral zone 101b of the combustion chamber 101.
When the engine 10 is in an intake stroke, the vortex mixed gas formed by the helical air inlet channel 121 enters the cylinder 11, the density of the exhaust gas is high, the exhaust gas and part of air are thrown into the peripheral area 101b close to the wall of the cylinder 11 under the action of vortex inertia, the air input by the tangential air inlet channel enters the central area 101a of the cylinder 11, and then the layering phenomenon of the exhaust gas and the air mixed gas is formed in the cylinder 11. In the present embodiment, when the engine 10 is in the compression stroke, the first combustion chamber 102 and the second combustion chamber 103 serve as a small combustion chamber 101, the central region 101a has a high oxygen content, the peripheral region 101b has a high exhaust gas content, and the exhaust gas inhibits chemical reaction, and as the pressure and temperature of the combustion chamber 101 instantaneously increase, the mixture gas in the central region 101a is first compression-ignited in the region above the first combustion chamber 102 and the first combustion chamber 102, and a plurality of ignition nuclei are formed, each of which ignites the mixture gas in the peripheral region 101b at the same time.
An injector 14 is provided on the cylinder head 12, and the injector 14 is used for injecting fuel, such as gasoline, but not limited thereto, into the combustion chamber 101. The fuel injector 14 is arranged in the middle of the cylinder head 12 along the axis of the cylinder 11, the nozzle of the fuel injector 14 faces the first combustion groove 102 of the piston 13, and when the engine is in a compression stroke, the fuel sprayed by the fuel injector 14 is in the area defined by the first combustion groove 102. In this embodiment, the cylinder head 12 is further provided with a glow plug, the glow plug is disposed near the fuel injector 14, and the glow plug is used for heating the working medium in the combustion chamber 101, so as to ensure that the fuel can be smoothly compression-ignited.
Fig. 2 is a schematic view of the structure of the engine of the present invention at the time of the intake stroke. Fig. 3 is a schematic view of the engine of the present invention in a compression stroke. FIG. 4 is a schematic flow diagram of the in-cylinder layered combustion method of the present invention. As shown in fig. 2, 3 and 4, the present invention also relates to a fuel in-cylinder split-layer combustion method which overcomes the problem of matching a complex ignition system required in the conventional gasoline engine and has a great potential in thermal efficiency improvement by adopting a higher compression ratio. The in-cylinder fuel split-layer combustion method of the present invention uses the engine 10 described above, and includes the steps of:
step one, when the engine 10 is in an intake stroke, exhaust gas and air form vortex mixed gas after passing through the spiral air inlet channel 121 and enter the cylinder 11, and the mixed gas throws the exhaust gas and part of the air into the peripheral area 101b close to the wall of the cylinder 11 under the action of vortex inertia.
Specifically, at the time of the intake stroke of the engine 10, the first intake valve 122 and the second intake valve are controlled to be opened, and at the same time, the opening degree of the exhaust gas control valve 126 is adjusted to control the amount of exhaust gas entering the helical intake passage 121, the exhaust gas and air form a vortex mixed gas after passing through the helical intake passage 121 and enter the cylinder 11, the exhaust gas due to the higher density throws the exhaust gas and a part of the air into the peripheral area 101b near the wall of the cylinder 11 under the action of vortex inertia, and the air input by the tangential intake passage enters the central area 101a of the cylinder 11.
And step two, injecting fuel into the cylinder 11 by using the injector 14 during the intake stroke, and mixing the gasified fuel with the exhaust gas and air in the peripheral area 101b under the action of vortex inertia.
Specifically, during the intake stroke of the engine 10, the injector 14 injects gasoline fuel into the cylinder 11, the gasoline fuel having a relatively high density is thrown into the peripheral region 101b near the wall of the cylinder 11 by the inertia of the swirl, and is mixed with the exhaust gas and the air, so that the gasoline, the exhaust gas, and the air mixture are stratified.
And step three, injecting fuel into the cylinder 11 by using the injector 14 during the compression stroke, and mixing the gasified fuel with the air in the central area 101a of the cylinder 11.
Specifically, during the compression stroke of the engine 10, the injector 14 injects a small amount of gasoline fuel into the cylinder 11, the injected gasoline fuel enters the first combustion groove 102 of the piston 13, and the first combustion groove 102 limits the gasoline fuel in the central region 101a of the cylinder 11, so as to prevent the gasoline fuel from diffusing to the peripheral region 101b of the cylinder 11, and the gasoline fuel is mixed with the air in the central region 101a to form a relatively stable mixture. It is worth mentioning that since the vortex gas mixture flows around the axis of the cylinder 11 in the peripheral area 101b, the vortex gas mixture is not damaged when the piston 13 moves toward the direction close to the cylinder head 12, which is beneficial to the layering advantage of the gas mixture.
And step four, in the end stage of the compression stroke, the mixed gas in the central area 101a is firstly subjected to compression ignition to form a plurality of fire nuclei, and the fire nuclei ignite the mixed gas in the peripheral area 101 b.
Specifically, at the end of the compression stroke, the temperature and pressure in the cylinder 11 increase, the mixed gas in the central area 101a of the cylinder 11 can be compression-ignited to form a plurality of fire nuclei due to the sufficient oxygen content, the exhaust gas in the peripheral area 101b of the cylinder 11 has a high content, the oxygen content in the exhaust gas is low, the carbon dioxide content is high, the carbon dioxide does not participate in the chemical reaction, the mixed gas can be used as an inhibitor of the chemical reaction, the chemical reaction rate of the gasoline fuel in the peripheral area 101b can be reduced, and the central area 101a of the cylinder 11 is in a multi-point simultaneous ignition state at the moment, and the mixed gas in the peripheral area 101b of the cylinder 11 can be ignited.
Further, when the engine 10 is in a cold start low temperature condition, the working medium (mixed gas of air and fuel) in the cylinder 11 is preheated by the preheating plug, so that the fuel can be smoothly and naturally ignited.
Further, when the engine 10 is in the low speed, medium, and low load conditions, the opening degree of the exhaust gas control valve 126 is controlled to be smaller than that when the exhaust gas control valve 126 is fully opened 1/3, and the injector 14 is controlled to inject fuel in a single injection during the intake stroke. In the present embodiment, the smaller opening degree of the exhaust gas control valve 126 can prevent the exhaust gas from rapidly diffusing in the cylinder 11 to form a homogeneous exhaust gas distribution due to the too low strength of the swirl, which is advantageous for smooth combustion.
Further, when the engine 10 is in the low-speed and high-load condition, the opening degree of the exhaust gas control valve 126 is controlled to be smaller than the opening degree of 1/2 when the exhaust gas control valve 126 is fully opened, and the injector 14 is controlled to inject the fuel a plurality of times during the intake stroke, preferably, the injector 14 injects the fuel 2 to 3 times, but not limited thereto.
Further, when the engine 10 is in the medium, high speed, medium, and low load conditions, the opening degree of the exhaust gas control valve 126 is controlled to be larger than 1/2 when the exhaust gas control valve 126 is fully opened, and the injector 14 is controlled to inject fuel in a single injection at the time of the intake stroke.
Further, when the engine 10 is in the medium, high speed, and large load condition, the opening degree of the exhaust gas control valve 126 is controlled to be smaller than the opening degree of the 1/2 when the exhaust gas control valve 126 is fully opened, and the injector 14 is controlled to inject the fuel a plurality of times in the intake stroke, and preferably, the injector 14 injects the fuel 2 to 3 times, but not limited thereto.
A cylinder cover 12 of an engine 10 is arranged on a cylinder 11, a piston 13 is movably arranged in the cylinder 11, a combustion chamber 101 is formed between the cylinder cover 12 and the piston 13, an oil injector 14 is arranged on the cylinder cover 12, the oil injector 14 is used for injecting fuel into the combustion chamber 101, a spiral air inlet channel 121 and an exhaust channel 123 are arranged on the cylinder cover 12, an exhaust gas guide channel 125 is connected between the spiral air inlet channel 121 and the exhaust channel 123, an exhaust gas control valve 126 for controlling the flow of exhaust gas is arranged on the exhaust gas guide channel 125, and when the engine 10 is in an air inlet stroke, the exhaust gas and air form vortex mixed gas after passing through the spiral air inlet channel 121 and enter the combustion chamber 101 of the cylinder 11. The engine 10 of the present invention is capable of avoiding strong knocking caused by the self-ignition of the end mixed gas of the gasoline fuel at a high compression ratio without modifying the existing gasoline fuel. Moreover, a higher compression ratio is significantly advantageous in terms of improvement in thermal efficiency. In addition, the control mode of gasoline stratified compression ignition provides a technical approach for controlling the non-equivalence ratio combustion processes such as gasoline lean combustion and the like.
The engine 10 of the present invention forms a stratified state of gasoline, exhaust gas, and air mixture in the cylinder 11 in a swirl manner, that is, a stratified state of low oxygen content in the peripheral region 101b and high oxygen content in the central region 101a is formed in the cylinder 11 by using the helical intake passage 121 in combination with exhaust gas having a relatively large molecular weight. Meanwhile, the inhibition effect of the waste gas on the chemical reaction is utilized to control the chemical reaction rate of the gasoline, and the mixed gas in the peripheral area 101b of the combustion chamber 101 is prevented from self-igniting firstly in the compression stroke. Moreover, the higher oxygen concentration in the central area 101a of the cylinder 11 is utilized to form gasoline and air mixed gas with fuel, so that local spontaneous combustion ignition can be ensured under high compression ratio, and the ignited area can be used as a large number of independent high-energy fire nuclei to ignite the mixed gas (gasoline, air and exhaust gas) in the peripheral area 101b after spontaneous combustion, unlike the detonation caused by the spontaneous combustion of the mixed gas at the tail end of the existing gasoline engine, because the spontaneous combustion ignition position occurs in the central area 101a of the cylinder 11.
The present invention is not limited to the specific details of the above-described embodiments, and various simple modifications may be made to the technical solution of the present invention within the technical idea of the present invention, and these simple modifications are within the protective scope of the present invention. The various features described in the foregoing detailed description may be combined in any suitable manner without departing from the scope of the invention. The invention is not described in detail in order to avoid unnecessary repetition.
Claims (12)
1. An engine is characterized by comprising a cylinder, a cylinder cover, a piston and an oil sprayer, wherein the cylinder cover is arranged on the cylinder, the piston is movably arranged in the cylinder, a combustion chamber is formed between the cylinder cover and the piston, the oil sprayer is arranged on the cylinder cover, the oil sprayer is used for spraying fuel into the combustion chamber, a spiral air inlet channel and an exhaust channel are arranged on the cylinder cover, an exhaust gas guide channel for controlling the flow of exhaust gas is connected between the spiral air inlet channel and the exhaust channel, and an exhaust gas control valve for controlling the flow of the exhaust gas is arranged on the exhaust gas guide channel; the end face of the piston is positioned in the combustion chamber, the end face of the piston is recessed towards the direction far away from the cylinder cover to form a first combustion groove and a second combustion groove, the first combustion groove is positioned in the middle of the piston, the second combustion groove is an annular groove, the second combustion groove is arranged along the circumferential direction of the first combustion groove, the combustion chamber comprises a central area close to the axis of the cylinder and a peripheral area close to the wall of the cylinder, the first combustion groove is positioned in the central area, the second combustion groove is positioned in the peripheral area, the cylinder cover is further provided with a tangential air inlet channel, vortex mixed gas formed by the spiral air inlet channel enters the peripheral area, air input by the tangential air inlet channel enters the central area, and when the engine is in the last stage of a compression stroke, the mixed gas in the central area is firstly subjected to compression ignition in the first combustion groove and the area above the first combustion groove to form a plurality of fire centers, each of the fire nuclei ignites the mixed gas in the peripheral region at the same time.
2. The engine of claim 1, characterized in that the fuel injector is arranged in the middle of the cylinder head along the axis of the cylinder.
3. The engine of claim 1, wherein a first intake valve is disposed in the helical intake passage, a tangential intake passage is further disposed in the cylinder head, a second intake valve is disposed in the tangential intake passage, and an exhaust valve is disposed in the exhaust passage.
4. The engine of claim 1, wherein a glow plug is further provided on the cylinder head, the glow plug being disposed proximate the fuel injector.
5. The engine of claim 1, wherein an ejector pipe is arranged at the end of the exhaust gas guide passage, the ejector pipe is arranged in the spiral air inlet passage, and the ejector pipe is arranged along the air inlet direction of the spiral air inlet passage.
6. A method of in-cylinder stratified charge compression ignition in a fuel cylinder, using the engine of any one of claims 1 to 5, comprising the steps of:
during the intake stroke of the engine, exhaust gas and air form vortex mixed gas after passing through the spiral air inlet channel, the mixed gas enters the cylinder, the exhaust gas and part of the air are thrown into the peripheral area close to the wall of the cylinder by the mixed gas under the action of vortex inertia, and meanwhile, the air in the tangential air inlet channel enters the central area of the cylinder;
fuel is sprayed into the cylinder by a fuel injector during an intake stroke, and the fuel is mixed with the waste gas and the air in the peripheral area under the action of vortex inertia after being gasified;
injecting fuel into the cylinder by using the fuel injector during a compression stroke, and mixing the gasified fuel with air in the central area of the cylinder; and
at the end of the compression stroke, the mixture in the central area is firstly compressed to form a plurality of fire nuclei, and the fire nuclei ignite the mixture in the peripheral area.
7. The method of fuel in-cylinder stratified combustion as claimed in claim 6, wherein the first combustion groove in the end surface of the piston is used to confine fuel to a central region of said cylinder when said engine is in a compression stroke.
8. The method of fuel in-cylinder stratified combustion as claimed in claim 7, wherein said cylinder is preheated by a glow plug when said engine is in a cold start cold temperature condition.
9. A method of fuel in-cylinder stratified combustion as claimed in claim 7, wherein when said engine is in a low speed, low load condition, the opening of said exhaust gas control valve is controlled to be less than 1/3 the opening of said exhaust gas control valve when fully open, and said injector is controlled to inject fuel a single time during the intake stroke.
10. The method of fuel in-cylinder stratified combustion as claimed in claim 7, wherein when said engine is in a low speed, high load condition, the opening degree of said exhaust gas control valve is controlled to be smaller than 1/2 the opening degree of said exhaust gas control valve is fully opened, and said injector is controlled to inject fuel a plurality of times during an intake stroke.
11. The method of in-cylinder fuel stratified combustion as claimed in claim 7, wherein when said engine is under medium speed, low load conditions, the opening degree of said exhaust gas control valve is controlled to be greater than 1/2 the opening degree of said exhaust gas control valve when fully opened, and said injector is controlled to inject fuel in a single injection during the intake stroke.
12. The method of in-cylinder fuel stratified combustion as claimed in claim 7, wherein when said engine is under a medium speed, large load condition, the opening degree of said exhaust gas control valve is controlled to be smaller than 1/2 the opening degree of said exhaust gas control valve is fully opened, and said injector is controlled to inject fuel a plurality of times during the intake stroke.
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| CN201811126324.4A CN110953066B (en) | 2018-09-26 | 2018-09-26 | Engine and in-cylinder split-layer combustion method |
| PCT/CN2019/072723 WO2020062738A1 (en) | 2018-09-26 | 2019-01-22 | Engine and method for stratified compression ignition of fuel in cylinder |
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| CN201811126324.4A CN110953066B (en) | 2018-09-26 | 2018-09-26 | Engine and in-cylinder split-layer combustion method |
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| CN113719341B (en) * | 2021-07-29 | 2022-11-29 | 东风商用车有限公司 | Jet-compression ignition combustion system of multi-partition combustion chamber |
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| FR2728939A1 (en) * | 1994-12-29 | 1996-07-05 | Inst Francais Du Petrole | IMPROVED METHOD AND APPARATUS FOR RECYCLING EXHAUST GAS AT THE INTAKE OF A FOUR-TIME ENGINE WITH COMMAND IGNITION |
| US5918577A (en) * | 1998-02-04 | 1999-07-06 | Ford Global Technologies, Inc. | Stratified exhaust residual engine |
| DE60115841T2 (en) * | 2000-01-25 | 2006-08-17 | Kabushiki Kaisha Toyota Chuo Kenkyusho | DIRECTLY INJECTED INTERNAL COMBUSTION ENGINE |
| DE10161853A1 (en) * | 2001-12-15 | 2003-06-26 | Daimler Chrysler Ag | Internal combustion engine with direct injection |
| DE10307456B4 (en) * | 2003-02-21 | 2007-10-31 | Audi Ag | Method and device for operating an internal combustion engine |
| JP2004270566A (en) * | 2003-03-10 | 2004-09-30 | Toyota Industries Corp | Premixed compression self-ignition type internal combustion engine |
| DE102004003900A1 (en) * | 2004-01-27 | 2005-08-18 | Adam Opel Ag | Combustion engine with piston cylinder has inlet channel with exhaust gas feedback and divider so that exhaust gas flows to cylinder wall and air or fuel mixture to center |
| CN1279271C (en) * | 2004-11-19 | 2006-10-11 | 清华大学 | Method of controlling charge compression Ignition of direct spray type gasoline engine homogeneous |
| JP5278399B2 (en) * | 2010-10-14 | 2013-09-04 | 株式会社デンソー | Intake control device for internal combustion engine |
| JP5845722B2 (en) * | 2011-08-25 | 2016-01-20 | マツダ株式会社 | Internal combustion engine |
| CN104533584B (en) * | 2014-10-30 | 2017-10-20 | 长城汽车股份有限公司 | engine intake and exhaust system and vehicle |
| CN104675506A (en) * | 2014-12-31 | 2015-06-03 | 大连理工大学 | Diesel engine multi-point distribution type guide bench combustion chamber |
| CN104791149B (en) * | 2015-04-21 | 2017-04-12 | 吉林大学 | Gasoline engine air and waste gas layered regulation device and method thereof |
| EP3533982B1 (en) * | 2016-12-01 | 2021-04-28 | Mazda Motor Corporation | Compression ignition gasoline engine |
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