CN109252990B - Air inlet temperature control system meeting requirements of gasoline compression ignition full working condition on air inlet temperature - Google Patents
Air inlet temperature control system meeting requirements of gasoline compression ignition full working condition on air inlet temperature Download PDFInfo
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- CN109252990B CN109252990B CN201811161783.6A CN201811161783A CN109252990B CN 109252990 B CN109252990 B CN 109252990B CN 201811161783 A CN201811161783 A CN 201811161783A CN 109252990 B CN109252990 B CN 109252990B
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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
- F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
- F02M31/02—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating
- F02M31/04—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture
- F02M31/06—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture by hot gases, e.g. by mixing cold and hot air
- F02M31/08—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture by hot gases, e.g. by mixing cold and hot air the gases being exhaust gases
- F02M31/087—Heat-exchange arrangements between the air intake and exhaust gas passages, e.g. by means of contact between the passages
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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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
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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
- F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
- F02M31/02—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating
- F02M31/04—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture
- F02M31/10—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture by hot liquids, e.g. lubricants or cooling water
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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
- F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
- F02M31/20—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for cooling
- F02M31/205—Control
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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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Abstract
The invention discloses an air inlet temperature control system meeting the requirement of the full working condition of gasoline compression ignition on air inlet temperature.A double-variable valve mechanism air inlet is connected with an air inlet main pipe, the air inlet main pipe is connected with an air compressor, an air outlet is connected with an exhaust main pipe, the exhaust main pipe is connected with a turbine, the turbine is connected with a post-processor, the air inlet main pipe is provided with an intercooler, the exhaust outlet of the post-processor is connected with two exhaust branches, one of the exhaust branches is provided with a second exhaust valve, and the other exhaust branch is provided with a first exhaust valve; the shell side water outlet of the exhaust heat exchanger is connected with the shell side water inlet of the intercooler, and the shell side water inlet of the exhaust heat exchanger is connected with the shell side water outlet of the intercooler; the intercooler shell side water inlet is connected with the first radiator water outlet, and the intercooler shell side water outlet is connected with the first radiator water inlet; and the water outlet of the intercooler shell pass is connected with the water inlet of the second radiator, the water inlet of the intercooler shell pass is connected with the water outlet of the engine cooling water channel, and the water outlet of the second radiator is connected with the water inlet of the engine cooling water channel.
Description
Technical Field
The invention relates to the field of internal combustion engines, in particular to an air inlet temperature control system meeting the requirement of the full working condition of gasoline compression ignition on air inlet temperature.
Background
The automobile industry is the prop industry of national economy, but with the increasing preservation quantity of automobiles, the problems of environmental pollution, energy shortage and the like caused by the automobiles increasingly arouse the attention of governments of various countries. In order to cope with the increasingly severe energy and environmental issues, countries have made stricter regulations on harmful emissions and fuel economy, and therefore, new challenges are presented to efficient clean combustion control techniques for internal combustion engines.
Gasoline, which is a conventional fossil fuel, is widely used in spark-ignition gasoline engines. However, the ignition type gasoline engine has the characteristics of large pumping loss, low compression ratio, easy detonation and the like, so that the gasoline fuel is difficult to be efficiently utilized in the gasoline engine. Compared with a gasoline engine, the diesel engine has the characteristics of high compression ratio, small pumping loss and the like. In addition, the characteristics of low rotating speed, sufficient fresh air amount, large reaction space and the like of the diesel engine are also beneficial to the full oxidation of the fuel. Compared with diesel fuel, the gasoline fuel has the characteristics of good volatility, long flame retardation and the like, and is beneficial to improving the NOx-Soot compromise relationship of the traditional diesel engine. Therefore, in recent years, research on control technologies for realizing efficient clean combustion in Gasoline Compression Ignition (GCI) on diesel engines has become a hot issue in the field.
With the progress of research, researchers find that the Gasoline Compression Ignition (GCI) has the problems of difficult cold start and unstable small-load combustion due to the fact that the gasoline fuel has low fuel activity, poor ignition performance and long flame retardation period caused by excessively high octane number; at high load, however, the problem arises that the Gasoline Compression Ignition (GCI) burns too early due to an increase in the fuel-air equivalence ratio. Researchers have found that intake air temperature is an important boundary condition for controlling ignition stability and ignition timing of Gasoline Compression Ignition (GCI). The improvement of the air inlet temperature of medium and small loads is beneficial to improving the combustion stability, the combustion efficiency and the combustion economy, and the reduction of the air inlet temperature of a large-load working condition is beneficial to inhibiting the early ignition and improving the compromise relation of NOx-root.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides an air inlet temperature control system which meets the requirement of the full working condition of gasoline compression ignition on air inlet temperature, fully utilizes the heat of engine exhaust gas and cooling water to control the air inlet temperature, can improve the combustion stability and combustion efficiency of the traditional gasoline compression ignition combustion mode under medium and small loads, and simultaneously inhibits premature ignition and improves the compromise relation of NOx-root under the working condition of large load.
The purpose of the invention is realized by the following technical scheme.
The invention relates to an air inlet temperature control system meeting the requirement of gasoline compression ignition full working condition on air inlet temperature, which comprises a double variable valve mechanism arranged in a compression ignition engine, wherein the air inlet of each cylinder of the double variable valve mechanism is connected with an air inlet manifold, all the air inlet manifolds are connected with the air outlet of an air inlet main pipe, the air inlet of the air inlet main pipe is connected with the air outlet of a compressor, and the air inlet of the compressor is connected with an air filter; each air cylinder exhaust port is connected with an exhaust manifold, all the exhaust manifolds are connected with an exhaust main pipe air inlet, the exhaust main pipe air outlet is connected with a turbine air inlet, the turbine air outlet is connected with a post-processor, an oil injector and a glow plug are arranged in each air cylinder of the double variable valve mechanism, and an air inlet temperature sensor is arranged at an air inlet of the air inlet main pipe;
the inlet manifold is provided with an intercooler, a branch gas pipe is connected between the inlet manifold and the exhaust manifold which are connected with the inlet end of the intercooler, and the branch gas pipe is provided with an EGR valve and an EGR one-way valve; the exhaust port of the post-processor is connected with two exhaust branches arranged in parallel, wherein one exhaust branch is provided with a second exhaust valve, and the other exhaust branch is provided with a first exhaust valve and an exhaust heat exchanger; the intercooler pipe pass is communicated with the air inlet main pipe, the exhaust heat exchanger pipe pass is communicated with the exhaust branch where the exhaust heat exchanger pipe pass is located, and the first exhaust valve is arranged at the air inlet of the exhaust heat exchanger;
the shell side water outlet of the exhaust heat exchanger is connected with the shell side water inlet of the intercooler through a water channel pipeline, a third water pump and a first water channel valve are arranged on the water channel pipeline, the shell side water inlet of the exhaust heat exchanger is connected with the shell side water outlet of the intercooler through the water channel pipeline, and a sixth water channel valve is arranged on the water channel pipeline; the intercooler shell side water inlet is connected with the first radiator water outlet through a water pipeline, a first water pump and a second water pipeline valve are arranged on the water pipeline, the intercooler shell side water outlet is connected with the first radiator water inlet through the water pipeline, and a seventh water pipeline valve is arranged on the water pipeline; the intercooler shell side water outlet is connected with the water inlet of the second radiator through a water path pipeline, a fifth water path valve is arranged on the water path pipeline, the intercooler shell side water inlet is connected with the water outlet of the engine cooling water channel through the water path pipeline, a third water path valve is arranged on the water path pipeline, a branch water pipeline is connected between the water path pipeline and the water inlet of the second radiator, the branch water pipeline is provided with a fourth water path valve, the water outlet of the second radiator is connected with the water inlet of the engine cooling water channel through the water path pipeline, and a second water pump is arranged on the water path pipeline.
First exhaust valve, second exhaust valve, exhaust heat exchanger, third water pump, first water route valve, intercooler, sixth water route valve constitute waste gas heating admission circulation, and this circulating water flow direction is: the water outlet of the exhaust heat exchanger → the third water pump → the first water path valve → the water inlet of the intercooler → the water outlet of the intercooler → the sixth water path valve → the water inlet of the exhaust heat exchanger → the water outlet of the exhaust heat exchanger, the exhaust flow passing through the exhaust heat exchanger is controlled by the first exhaust valve and the second exhaust valve to heat and control the temperature of the circulating water, and the heated circulating water heats the inlet air in the intercooler, so that the requirement of gasoline compression ignition on the improvement of the inlet air temperature under the medium and small load working conditions is met.
Second radiator, second water pump, third water route valve, intercooler, fifth water route valve constitute engine cooling water heating and admit air circulation, and this circulating water flow direction is: the water outlet of the second radiator → the second water pump → the water inlet of the engine cooling water channel → the water outlet of the engine cooling water channel → the third water path valve → the water inlet of the intercooler → the water outlet of the intercooler → the fifth water path valve → the water inlet of the second radiator → the water outlet of the second radiator, and the high-temperature cooling water of the engine is circulated to the intercooler to heat the intake air.
The second radiator, the second water pump and the fourth water way valve form an engine cooling water temperature control circulation, and the flow direction of the circulating water is as follows: the flow of cooling water flowing through the engine is controlled by adjusting the flow of the second water pump or the opening degree of the fourth waterway valve, so that the cooling water of the engine is always in the optimal temperature range.
First radiator, first water pump, second water route valve, intercooler, seventh water route valve constitute engine intake air cooling circulation, and this circulating water flow direction is: the water cooling system comprises a first radiator water outlet → a first water pump → a second water path valve → an intercooler water inlet → an intercooler water outlet → a seventh water path valve → a first radiator water inlet → a first radiator water outlet, and the flow of cooling water flowing through the intercooler is adjusted by adjusting the flow of the first water pump or the opening of the second water path valve or the opening of the seventh water path valve so as to ensure proper cooling intensity.
Compared with the prior art, the technical scheme of the invention has the following beneficial effects:
the invention comprises waste gas heating air inlet circulation, engine cooling water temperature control circulation and engine air inlet cooling circulation, different circulations are realized by controlling the states of a water pump and a water way valve, and the harsh requirement of Gasoline Compression Ignition (GCI) on the air inlet temperature under the full working condition is met by multi-circulation combined use.
The invention fully utilizes the heat of the waste gas and the engine cooling water to heat the inlet air, thereby improving the utilization rate of the fuel energy; and the intake pipeline does not need to add extra parts, and the strict requirement of the full working condition range of Gasoline Compression Ignition (GCI) on the intake temperature can be met only by reasonably adjusting the temperature and the flow of cooling water flowing through the intake intercooler.
The invention can improve the combustion stability and combustion efficiency of Gasoline Compression Ignition (GCI) by improving the air inlet temperature of medium and small loads, and can reduce the air inlet temperature of a large-load working condition to inhibit early ignition and improve the compromise relation of NOx-root. The invention does not need additional energy supply, does not need additional parts in the air inlet pipeline, and has the prospect of practical application and industrialization in the actual multi-cylinder heavy diesel engine.
Drawings
FIG. 1 is a schematic structural diagram of an intake air temperature control system for meeting the requirements of the gasoline compression ignition full working condition on the intake air temperature.
Reference numerals: the system comprises a first radiator 1, a first water pump 2, a fuel injector 3, an air inlet temperature sensor 4, a glow plug 5, a third water way valve 6, a second water way valve 7, a first water way valve 8, an intercooler 9, a fourth water way valve 10, a fifth water way valve 11, an air filter 12, an EGR one-way valve 13, an EGR valve 14, a compressor 15, a turbine 16, a post-processor 17, a third water pump 18, a first exhaust valve 19, a second exhaust valve 20, an exhaust heat exchanger 21, a sixth water way valve 22, a second radiator 23, a seventh water way valve 24, a second water pump 25 and a double variable valve mechanism 26.
Detailed Description
The technical solutions of the present invention are further described in detail with reference to the accompanying drawings and specific embodiments, which are only illustrative of the present invention and are not intended to limit the present invention.
As shown in figure 1, the intake temperature control system meeting the requirement of the gasoline compression ignition all-working condition on the intake temperature comprises a double variable valve mechanism 26 arranged in a compression ignition engine, and an injector 3 and a glow plug 5 are arranged in each cylinder of the double variable valve mechanism 26. Each air inlet of each cylinder of the double variable valve mechanism 26 is connected with an air inlet manifold, all the air inlet manifolds are connected with an air outlet of an air inlet main pipe, the air inlet main pipe is connected with an air outlet of the air compressor 15, and the air inlet of the air compressor 15 is connected with the air filter 12. And an air inlet temperature sensor 4 is arranged at the air outlet of the air inlet main pipe. Exhaust manifolds are connected to each cylinder exhaust port of the dual variable valve mechanism 26, all of which are connected to an exhaust manifold intake port, which is connected to a turbine 16 intake port.
The turbine 16 and the compressor 15 are connected through a shaft, an exhaust port of the turbine 16 is connected with a post-processor 17, an exhaust port of the post-processor 17 is connected with two exhaust branches which are arranged in parallel, one exhaust branch is provided with a second exhaust valve 20, and the other exhaust branch is provided with a first exhaust valve 19 and an exhaust heat exchanger 21. The intake manifold is provided with intercooler 9, be connected with the branch road trachea between 9 inlet connection's of intercooler inlet port and the exhaust manifold, the branch road trachea is provided with EGR valve 14 and EGR check valve 13. The tube side of the intercooler 9 is communicated with an air inlet main pipe, the tube side of the exhaust heat exchanger 21 is communicated with an exhaust branch where the tube side is located, and the first exhaust valve 19 is arranged at an air inlet of the exhaust heat exchanger 21. Wherein the intake intercooler 9 is used as an intake air heating device at the same time.
The exhaust heat exchanger 21 shell side water outlet H is connected with the intercooler 9 shell side water inlet B through a water channel pipeline, a third water pump 18 and a first water channel valve 8 are arranged on the water channel pipeline, the exhaust heat exchanger 21 shell side water inlet I is connected with the intercooler 9 shell side water outlet E through a water channel pipeline, and a sixth water channel valve 22 is arranged on the water channel pipeline. The 9 shell side water inlets B of intercooler are connected with the water outlet A of the first radiator 1 through a water pipeline, and the water pipeline is provided with a first water pump 2 and a second water valve 7, the 9 shell side water outlets E of intercooler are connected with the water inlet N of the first radiator 1 through a water pipeline, and the water pipeline is provided with a seventh water valve 24. 9 shell side delivery ports E of intercooler are connected with 23 water inlets K of second radiator through the water route pipeline, and are provided with fifth water route valve 11 on this water route pipeline, 9 shell side water inlets B of intercooler are connected with engine cooling water course delivery port D through the water route pipeline, and are provided with third water route valve 6 on this water route pipeline, are connected with branch water pipeline between the water route pipeline that this water route pipeline is connected with 23 water inlets K of second radiator, branch water pipeline is provided with fourth water route valve 10, 23 water outlets L of second radiator are connected with engine cooling water course water inlet M through the water route pipeline, and are provided with second water pump 2 on this water route pipeline. Wherein, the first radiator 1 and the second radiator 23 are both arranged on the windward side to be beneficial to heat dissipation.
The first exhaust valve 19, the second exhaust valve 20, the exhaust heat exchanger 21, the third water pump 18, the first water way valve 8, the intercooler 9 and the sixth water way valve 22 form an exhaust gas heating air inlet circulation, and the flow direction of the circulating water is as follows: the water outlet of the exhaust heat exchanger 21 → the third water pump 18 → the first water way valve 8 → the water inlet of the intercooler 9 → the water outlet of the intercooler 9 → the sixth water way valve 22 → the water inlet of the exhaust heat exchanger 21 → the water outlet of the exhaust heat exchanger 21, the exhaust flow passing through the exhaust heat exchanger 21 is controlled by the first exhaust valve 19 and the second exhaust valve 20 to heat and control the temperature of the circulating water, and the heated circulating water heats the intake air in the intercooler 9, so that the requirement of Gasoline Compression Ignition (GCI) on the improvement of the intake air temperature under the medium and small load working conditions is met. The working medium absorbs the waste gas of the engine through the exhaust heat exchanger 21 to heat, then heats the inlet air through the intercooler 9, the temperature of the cooling water can be adjusted by adjusting the opening degrees of the first exhaust valve 19 and the second exhaust valve 20, the flow of the cooling water flowing through the intercooler 9 can be adjusted by adjusting the flow of the third water pump 18 or the opening degree of the sixth water way valve 22 or the opening degree of the first water way valve 8, and the temperature and the flow of the inlet air can be comprehensively controlled to adjust the heating intensity so as to meet the inlet air temperature requirement of each working condition.
The second radiator 23, the second water pump 25, the third water way valve 6, the intercooler 9 and the fifth water way valve 11 form engine cooling water heating air inlet circulation, and the flow direction of the circulating water is as follows: the water outlet of the second radiator 23 → the second water pump 25 → the engine cooling water inlet → the engine cooling water outlet → the third water path valve 6 → the water inlet of the intercooler 9 → the water outlet of the intercooler 9 → the fifth water path valve 11 → the water inlet of the second radiator 23 → the water outlet of the second radiator 23, and the circulation circulates the high-temperature cooling water of the engine to the intercooler 9 to heat the intake air. The engine cooling water is heated and fed through the intercooler 9, and the flow of the cooling water flowing through the intercooler 9 is adjusted by adjusting the opening degree of the third water way valve 6 or the fifth water way valve 11 so as to ensure proper heating intensity.
The second radiator 23, the second water pump 25 and the fourth water channel valve 10 form an engine cooling water temperature control circulation, and the flow direction of the circulation water is as follows: the water outlet of the second radiator 23 → the second water pump 25 → the engine cooling water channel water inlet → the engine cooling water channel water outlet → the fourth water channel valve 10 → the second radiator 23 water inlet → the second radiator 23 water outlet, and the flow of the cooling water flowing through the engine is controlled by adjusting the flow of the second water pump 25 or the opening of the fourth water channel valve 10, thereby ensuring that the engine cooling water is always in the optimal temperature range. Through the fourth water way valve 10, the engine cooling water can directly enter the second radiator 23 without passing through the intercooler 9, so that the temperature of the engine cooling water can be independently controlled.
The first radiator 1, the first water pump 2, the second water way valve 7, the intercooler 9 and the seventh water way valve 24 form an engine air inlet cooling circulation, and the flow direction of the circulating water is as follows: the cycle of the first radiator 1 water outlet → the first water pump 2 → the second water path valve 7 → the intercooler 9 water inlet → the intercooler 9 water outlet → the seventh water path valve 24 → the first radiator 1 water inlet → the first radiator 1 water outlet is mainly used to reduce the intake air temperature under the large load condition. The flow of the cooling water flowing through the intercooler 9 is adjusted by adjusting the flow of the first water pump 2 or the opening of the second water way valve 7 or the opening of the seventh water way valve 24 to ensure proper cooling intensity, so that the engine is not ignited too early under heavy load. The cooling water takes away part of the engine intake heat through the intercooler 9 to reduce the intake temperature, and the heated cooling water radiates heat through the first radiator 1.
The intake temperature control system provided by the invention comprises an exhaust gas heating intake circulation, an engine cooling water temperature control circulation and an engine intake cooling circulation, different circulations are realized by controlling the states of a water pump and a water way valve, and the harsh requirement of Gasoline Compression Ignition (GCI) on the intake temperature under the full working condition is met by multi-circulation combined use. Under a large-load working condition, the temperature of cooling water is controlled within a target temperature range by adopting an engine cooling water temperature control cycle, and lower inlet air temperature is realized by adopting an inlet air cooling cycle, so that early ignition is inhibited, and the NOx-root compromise relation is improved; under the working conditions of medium and small loads, waste gas heating circulation and engine cooling water heating air inlet circulation can be adopted to heat inlet air, and the inlet air temperature is accurately controlled by controlling the opening of an exhaust valve, a water path valve and the rotating speed of a water pump, so that the combustion stability and the combustion efficiency under the medium and small loads are improved. Table 1 shows the method of implementing different water circuit cycles by the combined control of the water pump state and the water circuit valve state.
TABLE 1
In order to meet the requirement of the Gasoline Compression Ignition (GCI) on the intake air temperature under all working conditions, the four cycles can be used together. In a small-load working condition, waste gas heating air inlet circulation can be adopted firstly, after the temperature of cooling water in the engine reaches a target temperature range, the temperature control circulation of cooling water of the engine and the heating of cooling water of the engine are started for circulation, the air inlet cooling circulation is closed, the heating capacity of the air inlet under the small-load working condition is improved, and the requirement of GCI on the air inlet temperature under the small-load working condition is met; under the medium load working condition, engine cooling water is used for heating the air inlet circulation and the air inlet cooling circulation in a combined mode, and the flow of heating water and cooling water is controlled by controlling the opening degrees of the third water way valve 6 and the second water way valve 7, so that the requirement on the air inlet temperature under the medium load working condition is met; under a large-load working condition, an air inlet cooling circulation and an engine cooling water temperature control circulation are adopted, and the temperature of the engine cooling water is ensured to be normal while air inlet is cooled. Therefore, the invention can meet the strict requirement of the Gasoline Compression Ignition (GCI) on the intake temperature under the full working condition, has the potential of realizing the efficient and clean combustion of the Gasoline Compression Ignition (GCI) in the full working condition range, and has the prospect of practical application and industrialization in the actual multi-cylinder heavy diesel engine.
While the present invention has been described in terms of its functions and operations with reference to the accompanying drawings, it is to be understood that the invention is not limited to the precise functions and operations described above, and that the above-described embodiments are illustrative rather than restrictive, and that various changes and modifications may be effected therein by one skilled in the art without departing from the scope or spirit of the invention as defined by the appended claims.
Claims (5)
1. An air inlet temperature control system meeting the requirement of the gasoline compression ignition full working condition on air inlet temperature comprises a double variable valve mechanism (26) arranged in a compression ignition engine, wherein an air inlet of each cylinder of the double variable valve mechanism (26) is connected with an air inlet manifold, all the air inlet manifolds are connected with an air outlet of an air inlet main pipe, an air inlet of the air inlet main pipe is connected with an air outlet of a compressor (15), and an air inlet of the compressor (15) is connected with an air filter (12); each cylinder exhaust port is connected with an exhaust manifold, all the exhaust manifolds are connected with an exhaust main pipe air inlet, the exhaust main pipe air outlet is connected with a turbine (16) air inlet, the turbine (16) exhaust port is connected with a post-processor (17), and each cylinder of the double-variable valve mechanism (26) is internally provided with an oil injector (3) and a glow plug (5), and the double-variable valve mechanism is characterized in that an inlet air temperature sensor (4) is arranged at an air outlet of the inlet main pipe;
the intake manifold is provided with an intercooler (9), a branch air pipe is connected between the intake manifold and the exhaust manifold which are connected with the inlet end of the intercooler (9), and the branch air pipe is provided with an EGR valve (14) and an EGR one-way valve (13); an exhaust port of the post-processor (17) is connected with two exhaust branches which are arranged in parallel, wherein one exhaust branch is provided with a second exhaust valve (20), and the other exhaust branch is provided with a first exhaust valve (19) and an exhaust heat exchanger (21); the tube side of the intercooler (9) is communicated with an air inlet main pipe, the tube side of the exhaust heat exchanger (21) is communicated with an exhaust branch where the tube side is located, and the first exhaust valve (19) is arranged at an air inlet of the exhaust heat exchanger (21);
the shell side water outlet of the exhaust heat exchanger (21) is connected with the shell side water inlet of the intercooler (9) through a water channel pipeline, a third water pump (18) and a first water channel valve (8) are arranged on the water channel pipeline, the shell side water inlet of the exhaust heat exchanger (21) is connected with the shell side water outlet of the intercooler (9) through the water channel pipeline, and a sixth water channel valve (22) is arranged on the water channel pipeline; the shell side water inlet of the intercooler (9) is connected with the water outlet of the first radiator (1) through a water pipeline, a first water pump (2) and a second water way valve (7) are arranged on the water pipeline, the shell side water outlet of the intercooler (9) is connected with the water inlet of the first radiator (1) through the water pipeline, and a seventh water way valve (24) is arranged on the water pipeline; intercooler (9) shell side delivery port is connected with second radiator (23) water inlet through water pipeline, and is provided with fifth water route valve (11) on this water route pipeline, intercooler (9) shell side water inlet is connected with engine cooling water course delivery port through water pipeline, and is provided with third water route valve (6) on this water route pipeline, is connected with branch water pipeline between the water route pipeline that this water route pipeline is connected with second radiator (23) water inlet, branch water pipeline is provided with fourth water route valve (10), second radiator (23) water outlet is connected with engine cooling water course water inlet through water pipeline, and is provided with second water pump (2) on this water route pipeline.
2. The intake air temperature control system meeting the requirement of the gasoline compression ignition full working condition on the intake air temperature as claimed in claim 1, wherein the first exhaust valve (19), the second exhaust valve (20), the exhaust heat exchanger (21), the third water pump (18), the first water way valve (8), the intercooler (9) and the sixth water way valve (22) form an exhaust gas heating intake air circulation, and the flow direction of the circulation water is as follows: the water outlet of the exhaust heat exchanger (21) → the third water pump (18) → the first water way valve (8) → the water inlet of the intercooler (9) → the water outlet of the intercooler (9) → the sixth water way valve (22) → the water inlet of the exhaust heat exchanger (21 → the water outlet of the exhaust heat exchanger (21), the flow of exhaust gas flowing through the exhaust heat exchanger (21) is controlled through the first exhaust valve (19) and the second exhaust valve (20) to heat and control the temperature of circulating water, and the heated circulating water heats intake air in the intercooler (9), so that the requirement of gasoline compression ignition on the improvement of the intake air temperature under the medium and small load working conditions is met.
3. The intake air temperature control system meeting the requirement of the gasoline compression ignition full working condition on the intake air temperature as claimed in claim 1, wherein the second radiator (23), the second water pump (25), the third water way valve (6), the intercooler (9) and the fifth water way valve (11) form an engine cooling water heating intake air circulation, and the flow direction of the circulation water is as follows: the water outlet of the second radiator (23) → the second water pump (25) → the water inlet of the engine cooling water channel → the water outlet of the engine cooling water channel → the third water path valve (6) → the water inlet of the intercooler (9) → the water outlet of the intercooler (9) → the fifth water path valve (11) → the water inlet of the second radiator (23) → the water outlet of the second radiator (23), and the circulation circulates the high-temperature cooling water of the engine to the intercooler to achieve the purpose of heating the intake air.
4. The intake air temperature control system meeting the requirement of the gasoline compression ignition full working condition on the intake air temperature as claimed in claim 1, wherein the second radiator (23), the second water pump (25) and the fourth water way valve (10) form an engine cooling water temperature control cycle, and the flow direction of the circulating water is as follows: the water outlet of the second radiator (23) → the second water pump (25) → the water inlet of the engine cooling water channel → the water outlet of the engine cooling water channel → the fourth water channel valve (10) → the water inlet of the second radiator (23) → the water outlet of the second radiator (23), and the flow rate of cooling water flowing through the engine is controlled by adjusting the flow rate of the second water pump (25) or the opening degree of the fourth water channel valve (10), so that the cooling water of the engine is always in the optimal temperature range.
5. The intake air temperature control system meeting the requirement of the gasoline compression ignition full working condition on the intake air temperature as claimed in claim 1, wherein the first radiator (1), the first water pump (2), the second water way valve (7), the intercooler (9) and the seventh water way valve (24) form an engine intake air cooling cycle, and the flow direction of the circulating water is as follows: the cooling water circulation system comprises a first radiator (1) water outlet → a first water pump (2) → a second water path valve (7) → an intercooler (9) water inlet → an intercooler (9) water outlet → a seventh water path valve (24) → a first radiator (1) water inlet → a first radiator (1) water outlet, and cooling water flow passing through the intercooler (9) is adjusted by adjusting the flow of the first water pump (2) or the opening of the second water path valve (7) or the opening of the seventh water path valve (24) so as to ensure proper cooling intensity.
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| CN201811161783.6A CN109252990B (en) | 2018-09-30 | 2018-09-30 | Air inlet temperature control system meeting requirements of gasoline compression ignition full working condition on air inlet temperature |
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| CN201811161783.6A CN109252990B (en) | 2018-09-30 | 2018-09-30 | Air inlet temperature control system meeting requirements of gasoline compression ignition full working condition on air inlet temperature |
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| US20060112913A1 (en) * | 2004-11-26 | 2006-06-01 | Warren Edward L | Internal combustion engine |
| JP4548183B2 (en) * | 2005-03-31 | 2010-09-22 | マツダ株式会社 | Control device for spark ignition engine |
| DE102011006388A1 (en) * | 2011-03-30 | 2012-10-04 | Bayerische Motoren Werke Aktiengesellschaft | Method for operating a quantity-controlled internal combustion engine and internal combustion engine |
| CN103195618A (en) * | 2013-03-22 | 2013-07-10 | 上海交通大学 | Heat exchange device of air inlet and outlet pipe system |
| CN103644024B (en) * | 2013-11-28 | 2016-05-04 | 长城汽车股份有限公司 | A kind of car engine air admittance humidity control system |
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