CN218760118U - Gas supply system for promoting in-cylinder combustion based on jet swirl flame of pre-combustion chamber - Google Patents
Gas supply system for promoting in-cylinder combustion based on jet swirl flame of pre-combustion chamber Download PDFInfo
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- CN218760118U CN218760118U CN202223399007.4U CN202223399007U CN218760118U CN 218760118 U CN218760118 U CN 218760118U CN 202223399007 U CN202223399007 U CN 202223399007U CN 218760118 U CN218760118 U CN 218760118U
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Abstract
An air supply system for promoting in-cylinder combustion based on jet swirl flame of a precombustion chamber relates to an air supply system for promoting in-cylinder combustion. The utility model discloses a solve among the prior art prechamber ignition system's control process complicated, natural gas engine operating stability is low problem under the dynamic operating mode. After the high-concentration mixed gas in the pre-combustion chamber is ignited by the spark plug, rotational flow flame rotating along the axis of the combustion chamber is formed under the action of the guide vanes, the rotational flow flame ignites the thin mixed gas in the combustion chamber, the turbulent kinetic energy of the mixed gas in the combustion chamber is enhanced, the concentrated heat release of combustion in the cylinder is facilitated, the combustion duration is shortened, and the combustion stability of the natural gas engine in a thin combustion state is improved; meanwhile, the swirl flame does swirl motion in the combustion chamber, more local swirl is generated to strengthen heat transfer, lean combustion boundary widening of the natural gas engine is facilitated, and higher combustion thermal efficiency is obtained. The utility model belongs to the technical field of the natural gas engine burning.
Description
Technical Field
The utility model relates to a promote gas supply system of burning in the jar, concretely relates to gas supply system based on swirl flame promotes burning in the jar is sprayed in precombustion chamber belongs to natural gas engine burning technical field.
Background
Compared with a diesel engine and a gasoline engine, the natural gas engine has remarkable advantages in the aspects of economy and emission and also has remarkable disadvantages in the aspect of combustion stability. Because the flame propagation speed is slow when natural gas is combusted, and lean combustion is generally used in a natural gas engine to improve the thermal efficiency, the in-cylinder combustion rate is further slowed down. This results in significant cycle-to-cycle and cylinder-to-cylinder cycle differences in natural gas engines, increased control difficulties, and a high tendency for deterioration in unburned HC and CO emissions.
Increasing the ignition energy helps to improve the ignition reliability of the lean mixture and accelerate the in-cylinder combustion speed, so that the pre-combustion chamber ignition system is applied to a natural gas engine, namely, the rich mixture is organized in the pre-combustion chamber, after the mixture is ignited by a spark plug, the pressure and the temperature in the pre-combustion chamber are quickly increased, high-energy substances in the pre-combustion chamber are sent into the combustion chamber under the action of pressure difference, the lean mixture in the combustion chamber is ignited in a distributed mode, and finally, stable lean combustion is realized. However, with the widening of the lean combustion boundary, the natural gas engine still has obvious cycle-to-cycle fluctuation and reduced operation stability under the conditions of increased load and increased rotating speed.
The patent with publication number CN108331658B discloses an air supply system for improving natural gas engine frequency response based on pre-combustion chamber enrichment. However, the control process of the technical scheme is complex, the space of the precombustion chamber is limited, and the quality of the ignition mixed gas is increased, so that higher reliability requirements are provided for the air intake device.
In summary, the prechamber ignition system of the conventional natural gas engine realizes reliable ignition of lean mixture in a cylinder to a certain extent, but still needs to be optimized for the prechamber ignition system to improve combustion stability so as to meet the stability requirement of the natural gas engine under dynamic working conditions.
SUMMERY OF THE UTILITY MODEL
The utility model aims at solving the problem that the control process of precombustion chamber ignition system is complicated among the prior art, and natural gas engine operating stability is low under the dynamic operating mode. Further, an air supply system for promoting in-cylinder combustion based on a swirl jet flame in a precombustion chamber is provided.
The technical scheme of the utility model is that: an air supply system for promoting in-cylinder combustion based on swirl flame injection in a precombustion chamber comprises an air inlet channel, an air inlet valve, a cylinder cover, a spark plug, an exhaust channel, an exhaust valve, a piston and a cylinder sleeve, wherein the air inlet valve is arranged in the air inlet channel, the exhaust valve is arranged in the exhaust channel, the spark plug is vertically arranged on the cylinder cover, the piston is arranged in the cylinder sleeve, and a cavity between the piston and the cylinder cover forms a combustion chamber; it also includes a fuel injector, a precombustor, and a plurality of guide vanes.
The longitudinal section of the precombustion chamber is circular, and the central axis of the longitudinal section of the precombustion chamber is superposed with the central axis of the longitudinal section of the combustion chamber; the guide vanes are arranged at the outlet of the precombustion chamber in an annular array mode, a jet hole is formed in a gap between every two adjacent guide vanes, and the combustion chamber is communicated with the precombustion chamber through the jet hole; the fuel injector is mounted obliquely on the cylinder head.
Furthermore, the deflection angle alpha of the guide vane is 5-30 degrees.
Furthermore, the included angle between the fuel injector and the central axis of the longitudinal section of the precombustion chamber is 35-55 degrees.
Compared with the prior art, the utility model has the following effect:
1. the utility model forms thin natural gas mixture in the air inlet channel and enters the combustion chamber 9 through the air inlet valve 2; after the high-concentration mixed gas in the pre-combustion chamber 6 is ignited by the spark plug, a swirling flame which rotates along the axis of the combustion chamber 9 and moves downwards along the axis of the combustion chamber 9 is formed under the action of the guide vanes 6-1, the swirling flame ignites the lean mixed gas in the combustion chamber 9, the turbulent kinetic energy of the mixed gas in the combustion chamber 9 is enhanced, the concentrated heat release of in-cylinder combustion is facilitated, the combustion duration is shortened, and the combustion stability of the natural gas engine in a lean combustion state is improved.
2. After the swirl flame of the utility model is sprayed into the combustion chamber 9, the combustion heat release in the cylinder is strengthened, so that the dynamic characteristic of the natural gas engine is improved, the effective time of power promotion is favorably shortened, and the rotation speed fluctuation under variable working conditions is weakened; meanwhile, the swirling flame makes swirling motion in the combustion chamber 9, more local swirling flow is generated to enhance heat transfer, the expansion of lean combustion boundary of the natural gas engine is facilitated, and higher combustion thermal efficiency is obtained.
3. The jet hole 6-2 of the utility model can be widely applied to a large-bore natural gas engine, the flame propagation speed is accelerated by using swirl flame, and the emission of unburned HC and CO generated by insufficient combustion of the large-bore natural gas engine is reduced; compared with a method for dynamically controlling the gas concentration or the ignition energy of a spark plug, the method is simple to operate, has stronger universality, is beneficial to popularization and use on the similar type of engine, improves the economy and the emission of the natural gas engine, and is beneficial to saving the cost.
Drawings
Fig. 1 is a cross-sectional view of the present invention;
FIG. 2 is an enlarged view of a portion of FIG. 1 at I;
FIG. 3 is an isometric view of the guide vane 6-1 and the jet hole 6-2 of the present invention;
FIG. 4 is a top view of the guide vane 6-1 and the jet hole 6-2 of the present invention;
FIG. 5 is a view from the direction A of FIG. 4;
fig. 6 is a schematic longitudinal sectional view of the vortex gas flow generated in the combustion chamber 9 of the present invention;
fig. 7 is a schematic longitudinal cross-sectional view of a swirling flame in the combustion chamber 9 of the present invention;
fig. 8 is a schematic cross-sectional view of a swirling flame in the combustion chamber 9 of the present invention;
fig. 9 is a schematic cross-sectional view of the local swirl flow in the combustion chamber 9 of the present invention.
In the figure: 1. the device comprises an air inlet passage, 2, an air inlet valve, 3, a cylinder cover, 4, a spark plug, 5, a fuel injector, 6, a precombustion chamber, 6-1, a guide vane, 6-2, a jet hole, 7, an air outlet passage, 8, an exhaust valve, 9, a combustion chamber, 10, a piston, 11 and a cylinder sleeve.
Detailed Description
The technical solution of the present invention is further explained by the following embodiments with reference to the drawings.
The first embodiment is as follows: the embodiment is described with reference to fig. 1 and 2, the gas supply system based on the pre-combustion chamber jet swirl flame to promote in-cylinder combustion of the cylinder comprises an air inlet channel 1, an air inlet valve 2, a cylinder cover 3, a spark plug 4, an air outlet channel 7, an exhaust valve 8, a piston 10 and a cylinder sleeve 11, wherein the air inlet valve 2 is installed in the air inlet channel 1, the exhaust valve 8 is installed in the air outlet channel 7, the spark plug 4 is vertically installed on the cylinder cover 3, the head of the spark plug 4 extends into a pre-combustion chamber 9, the piston 10 is installed in the cylinder sleeve 11, and a combustion chamber 9 is formed by a cavity between the piston 10 and the cylinder cover 3; it also includes a fuel injector 5, a pre-chamber 6, and a number of guide vanes 6-1.
The longitudinal section of the precombustion chamber 6 is circular, and the central axis of the longitudinal section of the precombustion chamber 6 is superposed with the central axis of the longitudinal section of the combustion chamber 9; the guide vanes 6-1 are arranged at the outlet of the precombustion chamber 6 in an annular array mode, a jet hole 6-2 is formed in a gap between every two adjacent guide vanes 6-1, and the combustion chamber 9 is communicated with the precombustion chamber 6 through the jet hole 6-2; the fuel injector 5 is mounted obliquely on the cylinder head 3, and the nozzle orifice of the fuel injector 5 projects into the prechamber 9.
The second embodiment is as follows: in the present embodiment, the guide vane 6-1 of the present embodiment has a deflection angle α of 5 ° to 30 °, as described with reference to fig. 3 to 5. According to the arrangement, after the mixed gas in the pre-combustion chamber 6 is ignited by the spark plug, the swirl flame rotating along the axis of the combustion chamber 9 is formed under the action of the guide vanes 6-1, so that the turbulent kinetic energy of the mixed gas in the combustion chamber 9 is enhanced, the concentrated heat release of in-cylinder combustion is facilitated, the combustion duration is shortened, and the combustion stability of the natural gas engine in a lean combustion state is improved. Other components and connection relationships are the same as those in the first embodiment.
The third concrete implementation mode: referring to fig. 1, the fuel injector 5 of the present embodiment forms an angle of 35 ° to 55 ° with respect to the central axis of the longitudinal section of the precombustion chamber 6. Other components and connection relationships are the same as those in the first or second embodiment.
The fourth concrete implementation mode: the present embodiment will be described with reference to fig. 1, and the fuel injector 5 of the present embodiment employs high-pressure injection, preferably at an injection pressure of 3 to 5Mpa. Other components and connection relationships are the same as those in the first, second or third embodiment.
In the present embodiment, the natural gas concentration of the mixture in the precombustion chamber 6 is higher than the natural gas concentration in the intake passage 1
The fifth concrete implementation mode: the present embodiment will be described with reference to fig. 1, and the spark plug 4 of the present embodiment overlaps with the center axis of the longitudinal cross section of the precombustion chamber 6. Other components and connection relationships are the same as those in the first, second, third or fourth embodiment.
Specific embodiments of the present invention are further described below with reference to the accompanying drawings:
example 1: in the embodiment described with reference to fig. 1 to 8, the combustion in the combustion chamber 9 of the embodiment is implemented through the following processes:
the method comprises the following steps: premixing natural gas and air in the air inlet channel 1, adjusting the air inlet flow of the natural gas and the air, supplying air amount which exceeds the equivalent combustion of the natural gas, organizing thin mixed gas, and enabling the mixed gas to enter a combustion chamber 9 through an air inlet valve 2;
step two: as shown in fig. 6, after the intake stroke is finished, the intake valve 2 is closed, the piston 10 moves upwards, and the lean mixture generates vortex airflow under the action of the omega-shaped combustion chamber 9;
step three: as the piston 10 moves upwards, the fuel injector 5 injects a mixture of natural gas and air into the pre-chamber 6 before the piston 10 approaches top dead center; the fuel injector 5 adopts high-pressure injection, the injection pressure is 3-5 Mpa, and the concentration of the natural gas in the injected mixed gas is higher than that of the natural gas in the air inlet channel 1;
step four: 4. the spark plug 4 releases electric spark within the range of 15-45 degrees before the top dead center, and ignites the rich mixed gas in the precombustion chamber 6, and the rich mixed gas is rapidly combusted, so that the temperature and the pressure in the precombustion chamber 6 are rapidly increased, and a pressure difference is formed between the rich mixed gas and the combustion chamber 9;
step five: as shown in FIG. 7, under the action of the pressure difference, the flame in the precombustion chamber 6 enters the combustion chamber 9 through the jet holes 6-2;
step six: as shown in fig. 5, the deflection angle α of the guide vane 6-1 is 5 ° to 30 °; as shown in FIG. 8, the flame entering the combustion chamber 9 forms a swirling flame rotating along the axis of the combustion chamber 9 under the action of the guide vanes 6-1, and the lean mixture at the lower part of the jet hole 6-1 is ignited first;
step seven: as shown in fig. 9, the swirling flame forms a swirling motion in the cross section of the combustion chamber 9, the swirling motion being opposite to the swirling direction of the mixture (i.e., the swirling flow of the lean mixture) in the combustion chamber 9, i.e., two opposite air flows exist in the cross section of the combustion chamber 9, so that a plurality of partial swirls are formed in the cross section of the combustion chamber 9;
step eight: the existence of the local swirl strengthens the heat transfer phenomenon in the combustion chamber 9, and forms combustion flame which quickly diffuses towards the inner wall and the center of the combustion chamber 9 by taking the swirl flame area as a starting point; through the improvement of the propagation speed of flame in the combustion chamber 9 by the swirl flame, the in-cylinder combustion of the natural gas engine is strengthened, the concentrated heat release is promoted, the combustion duration is effectively shortened, and the combustion stability of the natural gas engine in a lean combustion state is finally and obviously improved.
In the embodiment, the swirling flame makes swirling motion in the combustion chamber 9, more local swirling enhanced heat transfer is generated, the natural gas engine is facilitated to widen the lean combustion boundary, and higher combustion thermal efficiency is obtained; compared with a method for dynamically controlling the gas concentration or the ignition energy of a spark plug, the method is simple to operate, has stronger universality, is beneficial to popularization and use on the similar type of engine, improves the economy and the emission of the natural gas engine, and is beneficial to saving the cost.
Principle of operation
The respective components are first assembled in the connection relationship in the first to seventh embodiments.
A thin natural gas mixture is formed in the air inlet passage and enters the combustion chamber 9 through the air inlet valve 2; after the high-concentration mixed gas in the pre-combustion chamber 6 is ignited by the spark plug, rotational flow flame rotating along the axis of the combustion chamber 9 is formed under the action of the guide vanes 6-1, the rotational flow flame ignites the lean mixed gas in the combustion chamber 9, the turbulent kinetic energy of the mixed gas in the combustion chamber 9 is enhanced, the combustion heat release in a cylinder is enhanced, the combustion duration is shortened, the combustion stability of the natural gas engine in a lean combustion state is improved, the dynamic characteristic of the natural gas engine is improved, the effective time of power improvement is favorably shortened, and the rotation speed fluctuation under variable working conditions is weakened.
The present invention has been disclosed in the above embodiments, but the present invention is not limited thereto, and any person skilled in the art will not depart from the technical solution of the present invention, and any simple modification, equivalent change and modification made by the technical spirit of the present invention to the above embodiments still belong to the technical solution scope of the present invention.
Claims (5)
1. An air supply system for promoting in-cylinder combustion based on swirl flame injection in a precombustion chamber comprises an air inlet channel (1), an air inlet valve (2), a cylinder cover (3), a spark plug (4), an exhaust channel (7), an exhaust valve (8), a piston (10) and a cylinder sleeve (11), wherein the air inlet valve (2) is installed in the air inlet channel (1), the exhaust valve (8) is installed in the exhaust channel (7), the spark plug (4) is vertically installed on the cylinder cover (3), the piston (10) is installed in the cylinder sleeve (11), and a combustion chamber (9) is formed by a cavity between the piston (10) and the cylinder cover (3); the method is characterized in that: the device also comprises a fuel injector (5), a precombustion chamber (6) and a plurality of guide vanes (6-1);
the longitudinal section of the precombustion chamber (6) is circular, and the central axis of the longitudinal section of the precombustion chamber (6) is superposed with the central axis of the longitudinal section of the combustion chamber (9); the guide vanes (6-1) are arranged at the outlet of the precombustion chamber (6) in an annular array manner, a jet hole (6-2) is formed in a gap between every two adjacent guide vanes (6-1), and the combustion chamber (9) is communicated with the precombustion chamber (6) through the jet hole (6-2); the fuel injector (5) is obliquely mounted on the cylinder head (3).
2. The gas supply system for boosting in-cylinder combustion based on a pre-chamber jet swirl flame as claimed in claim 1, wherein: the deflection angle alpha of the guide vane (6-1) is 5-30 degrees.
3. The pre-chamber jet swirl flame based in-cylinder combustion promoting air supply system of claim 2, wherein: the included angle between the fuel injector (5) and the central axis of the longitudinal section of the precombustion chamber (6) is 35-55 degrees.
4. The pre-chamber jet swirl flame based in-cylinder combustion promoting air supply system of claim 3, wherein: the injection pressure of the fuel injector (5) is 3-5 Mpa.
5. The pre-chamber jet swirl flame based air supply system for promoting in-cylinder combustion as claimed in claim 4, wherein: the spark plug (4) is superposed with the central axis of the longitudinal section of the precombustion chamber (6).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223399007.4U CN218760118U (en) | 2022-12-15 | 2022-12-15 | Gas supply system for promoting in-cylinder combustion based on jet swirl flame of pre-combustion chamber |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223399007.4U CN218760118U (en) | 2022-12-15 | 2022-12-15 | Gas supply system for promoting in-cylinder combustion based on jet swirl flame of pre-combustion chamber |
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| CN218760118U true CN218760118U (en) | 2023-03-28 |
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| CN202223399007.4U Active CN218760118U (en) | 2022-12-15 | 2022-12-15 | Gas supply system for promoting in-cylinder combustion based on jet swirl flame of pre-combustion chamber |
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