CN114353082A - Nozzle, combustor and gas heater - Google Patents
Nozzle, combustor and gas heater Download PDFInfo
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- CN114353082A CN114353082A CN202011073991.8A CN202011073991A CN114353082A CN 114353082 A CN114353082 A CN 114353082A CN 202011073991 A CN202011073991 A CN 202011073991A CN 114353082 A CN114353082 A CN 114353082A
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- burner
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- 238000002485 combustion reaction Methods 0.000 claims abstract description 212
- 238000002347 injection Methods 0.000 claims abstract description 170
- 239000007924 injection Substances 0.000 claims abstract description 170
- 239000007789 gas Substances 0.000 claims abstract description 115
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims abstract description 31
- 239000003546 flue gas Substances 0.000 claims abstract description 31
- 230000007246 mechanism Effects 0.000 claims abstract description 26
- 239000002737 fuel gas Substances 0.000 claims abstract description 22
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 22
- 239000007921 spray Substances 0.000 claims abstract description 11
- 238000005507 spraying Methods 0.000 claims abstract description 6
- 238000009826 distribution Methods 0.000 claims description 24
- 239000000779 smoke Substances 0.000 claims description 6
- 230000000694 effects Effects 0.000 description 16
- 239000000446 fuel Substances 0.000 description 8
- 238000002156 mixing Methods 0.000 description 7
- 239000001301 oxygen Substances 0.000 description 7
- 229910052760 oxygen Inorganic materials 0.000 description 7
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 6
- 239000000203 mixture Substances 0.000 description 4
- 239000000376 reactant Substances 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 239000003570 air Substances 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 239000012895 dilution Substances 0.000 description 2
- 238000010790 dilution Methods 0.000 description 2
- 239000003344 environmental pollutant Substances 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 231100000719 pollutant Toxicity 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000036632 reaction speed Effects 0.000 description 2
- 238000010992 reflux Methods 0.000 description 2
- 230000002269 spontaneous effect Effects 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000003287 bathing Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000000197 pyrolysis Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Classifications
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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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
Abstract
The invention discloses a nozzle, a combustor and a gas water heater, wherein the nozzle comprises a nozzle main body and a rotational flow mechanism; the nozzle body is provided with a spray inlet, a spray outlet and a spray channel communicated with the spray inlet and the spray outlet; the rotational flow mechanism is arranged in the injection channel and is used for forming rotational flow of the airflow flowing through the injection channel and then spraying the airflow. The burner of the invention enables the air and the fuel gas to be mixed more uniformly and improves the heat efficiency of the burner. And the rotational flow sprayed by the nozzle can be more effectively mixed with the preheated flue gas after being sprayed into the hearth, so that the combustor can more easily reach a high-temperature air combustion state.
Description
Technical Field
The invention relates to the technical field of burners, in particular to a nozzle, a burner and a gas water heater.
Background
At present, a nozzle of a combustor is single, and a straight hole injection mode is basically adopted, so that air and fuel gas are not uniformly mixed, and the thermal efficiency of the combustor is low.
The above is only for the purpose of assisting understanding of the technical solutions of the present invention, and does not represent an admission that the above is the prior art.
Disclosure of Invention
The main object of the present invention is to propose a nozzle which makes the burner more thermally efficient.
In order to achieve the purpose, the nozzle provided by the invention comprises a nozzle main body and a rotational flow mechanism;
the nozzle body is provided with an injection inlet, an injection outlet and an injection channel communicated with the injection inlet and the injection outlet;
the rotational flow mechanism is arranged in the injection channel and is used for forming rotational flow of the airflow flowing through the injection channel and then spraying the airflow.
In one embodiment, the swirling mechanism includes a guide vane provided to protrude from an inner wall surface of the injection passage.
In an embodiment, the swirling mechanism includes a plurality of guide vanes, the guide vanes are circumferentially arranged along the injection passage at intervals, and an extending direction of each guide vane forms an included angle with an axis of the injection passage.
In one embodiment, the plurality of guide vanes are uniformly arranged around the circumference of the injection passage.
In one embodiment, an included angle between the guide vane and the cross section of the injection channel is greater than or equal to 10 degrees and less than or equal to 60 degrees.
In one embodiment, the ratio of the height of the guide vane protruding from the inner wall surface of the injection passage to the inner diameter of the injection passage is greater than or equal to 0.05 and less than or equal to 0.5; and/or the ratio of the thickness of the guide vane to the height of the guide vane protruding out of the injection channel is greater than or equal to 0.1 and less than or equal to 1.
In one embodiment, the number n of the guide vanes and the extension length a of the guide vanes satisfy 0.5 × pi × D ≤ a × cos α × n ≤ 5 × pi × D, where D is the inner diameter of the injection passage, and α is the included angle between the guide vanes and the cross section of the injection passage.
In one embodiment, the guide vane is disposed at an end of the injection passage near the injection outlet.
In one embodiment, the guide vane is a swirl vane, a diagonal flow vane, or a helical vane.
The invention also provides a combustor, which comprises a combustion main body and a nozzle, wherein a combustion chamber is formed in the combustion main body, and the nozzle comprises a nozzle main body and a rotational flow mechanism;
the nozzle body is provided with an injection inlet, an injection outlet and an injection channel communicated with the injection inlet and the injection outlet;
the rotational flow mechanism is arranged in the injection channel and is used for forming rotational flow of the airflow flowing through the injection channel and then ejecting the airflow;
and the injection outlet of the nozzle is communicated with the combustion chamber and is used for injecting fuel gas and/or air into the combustion chamber so as to enable high-temperature air combustion to occur in the combustion chamber.
In one embodiment, the cross section of the combustion body is rectangular, and the burner comprises a plurality of nozzles which are arranged at intervals along the length direction of the combustion body.
In an embodiment, a plurality of the nozzles are disposed on both sides of the combustion main body in the width direction, and the plurality of the nozzles on both sides of the combustion main body in the width direction are staggered in the length direction of the combustion main body.
In one embodiment, the burner further comprises a gas distribution member mounted on the outer wall surface of the combustion body, the gas distribution member forming a gas distribution chamber, the injection inlets of the plurality of nozzles communicating with the gas distribution chamber, and the gas distribution chamber having a gas inlet.
In one embodiment, the combustion chamber comprises a high-temperature air combustion zone, a mixed combustion zone and a preheating combustion zone which are sequentially arranged and communicated along the vertical direction, and the nozzle is communicated with the mixed combustion zone and is used for jetting air and/or fuel gas to the mixed combustion zone and the high-temperature air combustion zone.
The invention also provides a gas water heater, which comprises a main body, a heat exchanger, a burner and a preheating burner, wherein a heat exchange chamber and a smoke outlet communicated with the heat exchange chamber are arranged in the main body; the heat exchanger is arranged in the heat exchange chamber;
the combustor comprises a combustion main body and a nozzle, wherein a combustion chamber is formed in the combustion main body, and the nozzle comprises a nozzle main body and a rotational flow mechanism;
the nozzle body is provided with an injection inlet, an injection outlet and an injection channel communicated with the injection inlet and the injection outlet;
the rotational flow mechanism is arranged in the injection channel and is used for forming rotational flow of the airflow flowing through the injection channel and then ejecting the airflow;
the injection outlet of the nozzle is communicated with the combustion chamber and is used for injecting fuel gas and/or air into the combustion chamber so as to enable high-temperature air combustion to occur in the combustion chamber;
the burner is arranged on the main body, and a flue gas outlet of the burner is communicated with the heat exchange chamber; and
the preheating burner is mounted on the main body and used for igniting the mixed gas and then delivering the mixed gas to a combustion chamber of the burner, and preheating the combustion chamber to a target temperature.
According to the invention, the rotational flow mechanism is arranged in the injection channel of the nozzle, so that the rotational flow mechanism is used for forming rotational flow of air flow flowing through the injection channel and then spraying out the air flow, when the nozzle sprays mixed gas of fuel gas and air, the air and the fuel gas are mixed more uniformly, and the heat efficiency of the combustor is improved. And the rotational flow sprayed by the nozzle can be more effectively mixed with the preheated flue gas after being sprayed into the hearth, so that the combustor can more easily reach a high-temperature air combustion state.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic structural view of a nozzle according to an embodiment of the present invention;
FIG. 2 is a simulation of the air flow trajectory at an angle of the nozzle of FIG. 1;
FIG. 3 is a simulated view of the airflow trajectory at another angle of the nozzle of FIG. 1;
FIG. 4 is a schematic structural view of an embodiment of the burner of the present invention;
FIG. 5 is an enlarged view of a portion of FIG. 4 at A;
fig. 6 is a schematic structural diagram of a gas water heater according to an embodiment of the present invention.
The reference numbers illustrate:
| reference numerals | Name (R) | Reference numerals | Name (R) | Reference numerals | Name (R) |
| 10 | Burner with a |
121 | |
310 | |
| 100 | Nozzle with a |
200 | |
320 | |
| 110 | |
210 | |
20 | |
| 111 | |
211 | High temperature |
21 | |
| 112 | |
212 | Preheating the |
22 | |
| 113 | Injection channel | 213 | |
30 | |
| 120 | |
300 | |
40 | Preheating burner |
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
It should be noted that if the description of "first", "second", etc. is provided in the embodiment of the present invention, the description of "first", "second", etc. is only for descriptive purposes and is not to be construed as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and/or" appearing throughout is to include three juxtapositions, exemplified by "A and/or B" including either scheme A, or scheme B, or a scheme in which both A and B are satisfied.
The invention provides a nozzle which can be used for a combustor so as to enable high-temperature air combustion to occur in the combustor.
In the embodiment of the present invention, as shown in fig. 1 to 5, the nozzle 100 includes a nozzle body 110 and a swirling mechanism 120. The nozzle body 110 has an injection inlet 111, an injection outlet 112, and an injection passage 113 communicating the injection inlet 111 and the injection outlet 112. The swirling mechanism 120 is provided in the injection passage 113, and the swirling mechanism 120 is configured to swirl the airflow flowing through the injection passage 113 and discharge the swirling airflow.
In the present embodiment, in order to reduce the resistance, the cross section of the injection channel 113 is circular or elliptical, and the injection channel 113 is a linear channel. The injection inlet 111 communicates with the gas distribution chamber 310 for introducing gas and/or air into the injection passage 113. The injection outlet 112 communicates with the combustion chamber 210 of the combustor 10 for injecting gas, air, or a mixture of gas and air into the combustion chamber 210. The swirling mechanism 120 may be a vane structure, and the vane structure may be fixed in the injection passage 113 or may be rotatably installed in the injection passage 113. The blade structure can be specifically helical blade, swirl blade, oblique flow blade, vortex blade etc. only need make when the air current passes through swirl mechanism 120, be given with the axis direction perpendicular or the rotational component that is the contained angle with injection channel 113 to make the air current in the injection channel 113 rotatory around its flow direction, form the swirl after from spouting export 112 blowout can.
According to the invention, the rotational flow mechanism 120 is arranged in the injection channel 113 of the nozzle 100, so that the rotational flow mechanism 120 is used for forming rotational flow of the airflow flowing through the injection channel 113 and then spraying the airflow, when the nozzle 100 sprays the mixed gas of fuel gas and air, the air and the fuel gas are mixed more uniformly, and the heat efficiency of the combustor 10 is improved. And the rotational flow sprayed from the nozzle 100 can be more effectively mixed with the preheated flue gas after being sprayed into the hearth, so that the combustor 10 can more easily reach a high-temperature air combustion state.
In an embodiment, referring to fig. 1 and 5, the swirling mechanism 120 includes a guide vane 121 protruding from an inner wall surface of the injection passage 113. The guide vane 121 and the injection main body 20 may be integrally or separately provided, and when the guide vane 121 and the injection main body 20 are separately provided, the guide vane 121 and the inner wall surface of the injection passage 113 may be fixedly connected by welding or the like. Specifically, the guide vane 121 is a swirl vane or a diagonal vane. The swirl vanes or diagonal flow vanes may be provided in plurality and spaced apart in the circumferential direction of the injection passage 113. A swirling flow channel or a diagonal flow channel is formed between two adjacent guide vanes 121, and when the air flow in the injection channel 113 passes through the guide vanes 121, a rotational component is imparted, thereby causing the air flow ejected from the injection outlet 112 to form a swirling flow. In another embodiment, the guide vanes 121 are helical vanes. The helical blade extends helically along the inner wall surface of the injection passage 113. In order to reduce the resistance, the protruding height of the spiral blade should be made smaller than the radius of the injection channel 113 so that the middle of the spiral blade forms a straight flow channel. By making the guide vane 121 a helical vane, when the air flow in the injection passage 113 close to the inner wall surface of the injection passage 113 passes through the helical vane, a rotational air volume is given, and the air flow ejected from the injection passage 113 forms a rotational flow while maintaining a single injection flow rate. By making the swirling flow mechanism 120 include the guide vane 121 protruding the inner wall surface of the injection passage 113, while making the nozzle 100 capable of effectively forming swirling flow ejection, the structure is simple, and the processing and molding are easy.
Further, the swirling mechanism 120 includes a plurality of guide vanes 121, the guide vanes 121 are arranged at intervals along the circumferential direction of the injection passage 113, and the extending direction of each guide vane 121 forms an included angle with the axis of the injection passage 113. The extending direction of each guide vane 121 forms an included angle with the axis of the injection channel 113, and the guide vane 121 may be specifically a swirl vane or an oblique flow vane, where the oblique flow vane refers to a vane extending in a straight line and forming an included angle with the axis of the injection channel 113. In order to make the ejected airflow form a swirl more effective, the guide vane 121 is preferably a swirl vane. The swirl vane means that the vane extends in a curve and is curved toward the injection inlet 111 so that the air flow passing through the swirl vane forms a swirl. The guide vanes 121 are arranged at intervals along the circumferential direction of the injection passage 113, a swirl passage is formed between two adjacent guide vanes 121, and the airflow in the injection passage 113 flows through the swirl passage to form a swirl flow and is ejected from the injection outlet 112. Compared with a spiral channel formed by a spiral blade, the air loss and pressure loss in the injection channel 113 are smaller, and the sprayed rotational flow effect is better.
In order to improve the injection effect of the swirling flow, in an embodiment, the distance between two adjacent guide vanes 121 is gradually increased from the injection inlet 111 to the injection outlet 112 side. Therefore, the airflow of the injection passage 113 passing through the guide vanes 121 is gradually diffused into a rotational flow, so that the air and the fuel gas are mixed more uniformly, and the heat efficiency of the burner 10 is improved. In other embodiments, the distance between two adjacent guide vanes 121 is uniformly set from the injection inlet 111 to the injection outlet 112 side. So for injection passage 113 is the gathering form through guide vane 121's air current, makes the whirl that forms more stable and gather together, thereby spout into furnace by this nozzle 100 spun whirl after, can mix with preheating the flue gas for a long time steadily, thereby makes combustor 10 change and reaches the high temperature air combustion state.
Further, referring to fig. 1 to 5, the plurality of guide vanes 121 are uniformly arranged around the circumferential direction of the injection passage 113. Thus, the swirl passages formed between two adjacent guide vanes 121 are the same. Therefore, when the airflow in the injection channel 113 flows through the guide vanes 121, the airflow close to the inner peripheral wall of the injection channel 113 is uniformly divided into a plurality of rotational flows, and then the airflow is uniformly rotated around the axis of the injection channel 113 after being sprayed out from the injection outlet 112, so that a stable rotational flow is formed, the gas and the air are mixed more uniformly, the mixing time with the preheated flue gas in the hearth is longer, and the high-temperature air combustion state is easier to achieve.
In one embodiment, the angle between the guide vane 121 and the cross section of the injection channel 113 is greater than or equal to 10 degrees and less than or equal to 60 degrees. The angle between the guide vane 121 and the cross section of the injection passage 113 may be 10 degrees, 15 degrees, 20 degrees, 25 degrees, 30 degrees, 35 degrees, 45 degrees, 50 degrees, 55 degrees, 60 degrees, or the like. It is understood that the cross-section of the injection channel 113 refers to a cross-section perpendicular to the axis of the injection channel 113. When the angle between the guide vane 121 and the cross section of the injection passage 113 is less than 10 degrees, the resistance and pressure loss of the air flow passing through the guide vane 121 are made larger, thereby causing a large wind loss. When the included angle between the guide vane 121 and the cross section of the injection passage 113 is greater than 60 degrees, the guide vane 121 tends to be parallel to the axis of the injection passage 113, so that the airflow is not easy to form a rotational flow or the rotational flow is not easy to form after passing through the guide vane 121. When the included angle between the guide vane 121 and the cross section of the injection passage 113 is greater than or equal to 10 degrees and less than or equal to 60 degrees, the wind loss and the wind resistance are reduced while the rotational flow is effectively formed, and the rotational flow air quantity is increased.
In one embodiment, the ratio of the height of the guide vane 121 protruding from the inner wall surface of the injection passage 113 to the inner diameter of the injection passage 113 is greater than or equal to 0.05 and less than or equal to 0.5. The ratio of the height of the guide vane 121 projecting from the inner wall surface of the injection passage 113 to the inner diameter of the injection passage 113 may be specifically 0.05, 0.08, 0.1, 0.15, 0.2, 0.35, 0.4, 0.5, or the like. When the ratio of the height of the guide vane 121 protruding the inner wall surface of the injection passage 113 to the inner diameter of the injection passage 113 is less than 0.05, the protruding height of the guide vane 121 is too small, which makes the forming difficult and makes the swirling flow poor. When the ratio of the height of the guide vane 121 protruding the inner wall surface of the injection passage 113 to the inner diameter of the injection passage 113 is greater than 0.5, the protruding height of the guide vane 121 is too high, so that the passage in the middle of the injection passage 113, in which the guide vane 121 is not arranged, is too small, the overall wind resistance and pressure loss are increased, the air volume is reduced, and the wind speed does not meet the requirement. The ratio of the height of the guide vane 121 protruding the inner wall surface of the injection passage 113 to the inner diameter of the injection passage 113 is greater than or equal to 0.05 and less than or equal to 0.5, so that the swirl flow volume and the wind speed sprayed from the nozzle 100 can be ensured while the swirl flow is effectively formed, and the combustion effect of the combustor 10 can be further improved.
In another embodiment, the ratio of the thickness of the guide vane 121 to the height of the guide vane 121 protruding the injection channel 113 is greater than or equal to 0.1 and less than or equal to 1. The ratio of the thickness of the guide vane 121 to the height of the guide vane 121 protruding the injection passage 113 may be specifically 0.1, 0.3, 0.5, 0.75, 0.8, 0.95, 1, or the like. When the ratio of the thickness of the guide vane 121 to the height of the guide vane 121 protruding out of the injection channel 113 is less than 0.1, the thickness of the guide vane 121 is too thin, which is not easy to process, on the one hand, the guide vane 121 has low strength and is easy to damage, and noise is easy to generate. When the ratio of the thickness of the guide vane 121 to the height of the guide vane 121 protruding out of the injection passage 113 is greater than 1, the thickness of the guide vane 121 is too thick, and the distance between two adjacent guide vanes 121 is reduced, so that the resistance is increased, and the effect of forming the rotational flow is worse. And when the ratio of the thickness of the guide vane 121 to the height of the guide vane 121 protruding out of the injection channel 113 is greater than or equal to 0.1 and less than or equal to 1, on one hand, the processing is easy, the guide vane 121 has high strength, is not easy to damage, reduces noise, and on the other hand, the effect of forming the rotational flow is better. By combining the embodiment that the ratio of the height of the guide vane 121 protruding the inner wall surface of the injection channel 113 to the inner diameter of the injection channel 113 is greater than or equal to 0.05 and less than or equal to 0.5, the thickness and the protruding height of the whole guide vane 121 are appropriate, the swirling effect sprayed by the nozzle 100 is better while the processing is easy, and the requirement of the air volume can be met.
In one embodiment, the number n of the guide vanes 121 and the extension length a of the guide vanes 121 satisfy 0.5 × pi × D ≦ a × cos α × n ≦ 5 × pi × D, where D is the inner diameter of the injection passage 113, and α is the angle between the guide vanes 121 and the cross section of the injection passage 113.
It is understood that a × cos α refers to a projected length of the guide vane 121 on the cross section of the injection passage 113. The extending length of each guide vane 121 is generally made uniform. A × cos α × n refers to the sum of the projected lengths of all guide vanes 121 on the cross section of the injection channel 113. 0.5 × π × D refers to half the circumference of the injection channel 113, and 5 × π × D refers to 5 times the circumference of the injection channel 113. The number of the guide vanes 121 may be 5 to 10. When a × cos α × n is less than 0.5 × pi × D, it indicates that the number of the guide vanes 121 is too small, and the included angle between the guide vanes 121 and the cross section of the injection passage 113 is too large, so that the effect of the plurality of guide vanes 121 forming the swirling flow to the air flow in the injection passage 113 is not significant. When a × cos α × n is greater than 5 × pi × D, it indicates that the density of the guide vanes 121 is too high, so that the pressure loss and the wind resistance of the airflow passing through the injection passage 113 are large, the effect of forming the rotational flow by the airflow ejected from the ejection outlet 112 is poor, and the air volume and the wind speed do not meet the requirements. When the number n of the guide vanes 121 and the extension length a of the guide vanes 121 satisfy 0.5 × pi × D or less and a × cos α × n or less and 5 × pi × D or less, the swirl flow ejected from the ejection outlet 112 has good stability and large wind speed and wind volume, and further the combustion efficiency in the combustor 10 is high, and when high-temperature air is generated in the combustor 10 for combustion, the mixing of the mixed gas ejected from the nozzle 100 and the preheated flue gas is effectively enhanced, so that the combustor 10 can easily reach a high-temperature air combustion state. By combining the above embodiment in which the included angle between the guide vane 121 and the cross section of the injection channel 113 is greater than or equal to 10 degrees and less than or equal to 60 degrees, the air flow sprayed by the nozzle 100 effectively forms a rotational flow, and simultaneously reduces wind loss and wind resistance, and greatly improves the rotational flow air quantity and the wind speed.
In one embodiment, referring to fig. 1 and 5 again, the guide vane 121 is disposed at an end of the injection channel 113 near the injection outlet 112. When guide vanes 121 are fully distributed in the whole injection passage 113, the airflow passing through the injection passage 113 is subjected to rotational flow action through the guide vanes 121 in the whole process, so that the wind resistance and pressure loss can be increased, and the ejected rotational flow air quantity and the ejected wind speed are smaller. However, when the guide vane 121 is only disposed at one end of the injection passage 113 close to the injection inlet 111, although wind resistance and wind loss can be reduced, after the air flow passes through the guide vane 121 to form a rotational flow, the air flow needs to pass through a path in the injection passage 113, and thus the rotational flow effect is greatly reduced. Through making guide vane 121 locate the one end that is close to jet outlet 112 in injection passage 113, when reducing windage and wind loss, make the effective stable formation whirl of jet outlet 112 spun air current, and wind speed and amount of wind are big, can satisfy the user demand.
In a preferred embodiment, the inner diameter D of the injection passage 113 of the nozzle 100 is 4mm, and the length of the injection passage 113 is 8 mm. The number of the guide vanes 121 is 8, the included angle between the guide vanes 121 and the cross section of the injection passage 113 is 30 °, the height of the guide vanes 121 protruding the inner wall surface of the injection passage 113 is 0.6mm, the thickness of the guide vanes 121 is 0.16mm, and the length of the guide vanes 121 is 1.81 mm. Therefore, the swirl flow sprayed from the whole nozzle 100 is more stable, the air volume is larger, and the combustion effect of the burner 10 is better.
The present invention further provides a burner 10, as shown in fig. 4 and 5, the burner 10 includes a combustion main body 200 and a nozzle 100, a combustion chamber 210 is formed in the combustion main body 200, the specific structure of the nozzle 100 refers to the above embodiments, and the injection outlet 112 of the nozzle 100 is communicated with the combustion chamber 210 and is used for injecting gas and/or air into the combustion chamber 210, so as to enable high temperature air combustion to occur in the combustion chamber 210.
In the present embodiment, the burner 10 is suitable for gas water heaters and related products and devices such as wall-mounted gas furnaces that use gas combustion to generate high-temperature hot water for home bathing and heating, and will be hereinafter described as an example of application to gas water heaters for convenience of understanding.
The high-temperature air combustion is mainly characterized in that: the chemical reactions mainly occur in a high-temperature low-oxygen environment, the temperature of the reactants is higher than the autoignition temperature of the reactants, the maximum temperature rise in the combustion process is lower than the autoignition temperature of the reactants, and the volume fraction of oxygen is diluted to an extremely low concentration by the combustion products. Compared with conventional combustion, in the combustion state, the pyrolysis of fuel is inhibited, the flame thickness is thickened, and the flame front surface disappears, so that the temperature of the whole hearth is uniform, the combustion peak temperature is low, the noise is low, and the emission of pollutants NOx and CO is greatly reduced. However, achieving high temperature air combustion requires certain conditions: the oxygen concentration at any position in the furnace is required to be ensured to be lower than a certain value, generally lower than 5% -10%, the fuel gas is ensured to be fully combusted and uniformly combusted, the temperature is higher than the self-ignition point of the fuel, and the self-ignition is maintained.
The shape of the combustion body 200 may be square, cylindrical, etc., and may be selected and designed according to actual needs, and is not particularly limited herein. The combustion chamber 210 can be divided into a high-temperature air combustion area 211, and when the gas is combusted at high temperature in the high-temperature air combustion area 211, the heat generated after the combustion is discharged through a flue gas outlet, and then the heat can be exchanged with a heat exchanger of a gas water heater, so as to realize the preparation of hot water. Due to the upward flow characteristic of the flue gas, the high-temperature air combustion zone 211 can be positioned in the upper half part of the whole combustor 10, and the flue gas is more favorably discharged. And in order to further increase the exhaust rate of the flue gas, the upper end of the combustion body 200 is open-ended to form a flue gas outlet. Of course, high temperature air combustion may be performed in the entire combustion chamber 210. The injection outlet 112 of the nozzle 100 communicates with the combustion chamber 210 to inject gas and/or air into the combustion chamber 210.
It is understood that the preheating combustion of the combustion chamber 210 can be achieved by additionally providing the preheating burner 40 and an ignition device for igniting the preheating burner 40. The heating temperature is controlled to heat the temperature in the combustion chamber 210 to the target temperature, and thus, the high-temperature preheating of the high-temperature air combustion zone 211 is achieved. When the high-temperature air combustion area 211 of the combustion chamber 210 is preheated to the target temperature, the nozzle 100 sprays fuel gas and/or air to be effectively and fully mixed with the high-temperature flue gas in the combustion chamber 210, and the high-temperature flue gas ignites the fuel gas, so that complete and continuous high-temperature air combustion can be realized, and the generation of pollutants is reduced. Specifically, the combustor 10 further includes a temperature measuring device, and the temperature measuring device is disposed in the high-temperature air combustion area 211, the flue gas outlet, or another cavity communicated with the flue gas outlet. The temperature measuring device is used for detecting whether the temperature of the gas in the high-temperature air combustion area 211 reaches a target temperature or not, if not, the temperature in the high-temperature air combustion area 211 needs to be increased, and the temperature of the air and the gas which enter the preheating burner 40 for combustion can be adjusted according to the flow rate or the ratio of the gas to the air. By detecting the temperature, the preheating burner 40 can automatically adjust the heat load according to the temperature required by the high-temperature air combustion area 211 to achieve the effect of quickly preheating the high-temperature air combustion area 211 while ensuring low CO and NOX emissions throughout the combustion process. The temperature measuring device may be a temperature sensor.
Gas and air are mixed in a premixer according to a certain proportion, the mixed gas is conveyed to a preheating burner 40 for combustion, an ignition device is used for ignition, the preheating burner 40 is used for preheating combustion so as to preheat the high-temperature air combustion zone 211 at a high temperature, a temperature measuring device is used for measuring whether the high-temperature air combustion zone 211 reaches a set temperature, after the set temperature is reached, a gas injection device injects the mixed gas of the gas and the air into a combustion chamber 210, or independently injects the gas or the air, so that most of the gas is injected into the high-temperature air combustion zone 211 and is combined with the high-temperature flue gas in the high-temperature air combustion zone 211, the high-temperature flue gas ignites the gas, thereby realizing the high-temperature air combustion in the high-temperature air combustion zone 211, and because the gas is injected through a nozzle 100, a entrainment effect can be formed in the high-temperature air combustion zone 211, so that an injection combustion zone and a flue gas reflux zone are formed in the high-temperature air combustion zone 211, part of the flue gas is intensively circulated in the high-temperature air combustion zone 211, and then the injected fuel gas and air are fully diluted to form lower oxygen concentration, so that the combustion reaction speed is reduced, the higher temperature in the high-temperature air combustion zone 211 is maintained, the temperature is higher than the self-ignition point of the fuel, and the self-ignition is realized. As such, the present embodiment satisfies the condition of high-temperature air combustion (mld combustion): high-temperature preheating air is matched with high-speed jet flow to realize entrainment of high-temperature flue gas and dilution of air jet flow, so that the oxygen concentration is lower than a certain value, and the temperature is higher than the self-ignition point of fuel. After the rotational flow jet flow sprayed from the nozzle 100 of the above embodiment is sprayed into the combustion chamber 210, the rotational flow jet flow can be more effectively, continuously and fully mixed with the preheated flue gas, so that the combustor 10 can more easily reach a high-temperature air combustion state, the effective working condition range of the combustor 10 is widened, the problem that the combustor 10 cannot reach the high-temperature air combustion state under partial working conditions is solved, and the reliability of the combustor 10 is improved.
Further, referring to fig. 4, the cross-section of the combustion main body 200 is rectangular, and the burner 10 includes a plurality of nozzles 100, and the plurality of nozzles 100 are spaced apart along the length direction of the combustion main body 200.
In the present embodiment, the plurality of nozzles 100 are installed on a side wall surface of the combustion body 200 extending in the length direction, that is, on a peripheral side plate. The plurality of nozzles 100 may be provided on the same side wall surface or on both opposite side walls of the combustion body 200. The gas ejected from the plurality of nozzles 100 may be the same or different, for example, the plurality of nozzles 100 may eject a mixed gas of gas and air at the same time, or a plurality of nozzles 100 may eject gas, a plurality of nozzles 100 may eject air, or a plurality of nozzles 100 may eject a mixed gas of gas and air, and a plurality of nozzles 100 may eject gas or air. It is only necessary to inject a desired gas into the combustion chamber 210 so that high-temperature air combustion occurs in the combustion chamber 210. The interval between two adjacent nozzles 100 may be the same or different. Through setting up a plurality of nozzles 100 and jetting gas and/or air, can take place the entrainment effect in high temperature air combustion area 211 on the one hand, on the other hand makes the gas mixture of gas and air can distribute in combustion chamber 210 evenly, is favorable to carrying out abundant even burning in high temperature air combustion area 211.
In one embodiment, as shown in fig. 4, a plurality of nozzles 100 are disposed on both sides of the combustion body 200 in the width direction, and the plurality of nozzles 100 on both sides of the combustion body 200 in the width direction are staggered in the length direction of the combustion body 200. All set up a plurality of nozzles 100 through both sides on burning main part 200 width direction, and make a plurality of nozzles 100 of burning main part 200 width direction both sides crisscross the arranging in the length direction of burning main part 200, then can spray gas and/or air to the combustion chamber 210 in from the relative both sides of burning main part 200, improve gas injection volume on the one hand, on the other hand makes the mist evenly distributed who is favorable to gas and air in combustion chamber 210, combines to burn with high temperature air fully.
In one embodiment, the burner 10 further includes a gas distributing member 300 installed on an outer wall surface of the combustion body 200, the gas distributing member 300 forming a gas distributing chamber 310 therein, the injection inlets 111 of the plurality of nozzles 100 communicating with the gas distributing chamber 310, the gas distributing chamber 310 having a gas inlet 320.
In the present embodiment, the gas distributing member 300 may be integrally formed with the combustion body 200 or may be separately formed. The gas distribution member 300 and the combustion body 200 may be fixedly coupled by means of screws, welding, etc. By forming the gas distribution chamber 310 in the gas distribution member 300, a mixed gas of gas and air, or gas or air, can be introduced into the gas distribution chamber 310, and then distributed to the plurality of nozzles 100, and then injected into the combustion chamber 210. Therefore, the injection flow of the plurality of nozzles 100 is more uniform, the flow rate of the gas injected by each nozzle 100 can be ensured, and the combustion of the whole combustion chamber 210 is more stable. It will be appreciated that the nozzle 100 is sealingly connected to both the gas distributor 300 and the combustion body 200, thereby ensuring operational stability and safety of the overall combustor 10. A pressure measuring port may be further disposed at the gas inlet 320 of the gas distribution chamber 310, so as to detect the gas pressure at any time and ensure the combustion stability and safety. The gas distribution member 300 may have a gas distribution pipe such that the gas distribution pipe extends along the length of the combustion body 200. The gas distribution pipe may be a square pipe, which facilitates installation between the gas distribution pipe and the combustion main body 200.
In an embodiment, as shown in fig. 6, the combustion chamber 210 includes a high temperature air combustion zone 211, a mixing combustion zone 213 and a preheating combustion zone 212 which are sequentially arranged and communicated in a vertical direction, and the nozzle 100 is communicated with the mixing combustion zone 213 for injecting air and/or fuel gas to the mixing combustion zone 213 and the high temperature air combustion zone 211.
In this embodiment, the nozzle 100 may inject the gas and/or air directly into the high temperature air combustion zone 211, or may inject the gas and/or air into the mixed combustion zone 213 of the combustion chamber 210, such that the airflow then flows into the high temperature air combustion zone 211. The high-temperature air combustion zone 211, the mixed combustion zone 213 and the preheating combustion zone 212 may be arranged in sequence from top to bottom. The preheat burner 40 may be correspondingly disposed within the preheat combustion zone 212. By dividing the combustion chamber 210 into the preheating burner 40, the mixed combustion zone 213 and the high temperature air combustion zone 211, the high temperature flue gas generated by the preheating burner 40 enters the high temperature air combustion zone 211, so that the high temperature air combustion zone 211 reaches the temperature required by the high temperature air combustion. The nozzle 100 injects fuel gas and/or air into the mixed combustion zone 213, and the mixed combustion zone 213 belongs to a transition combustion zone, so that the unburned fuel gas in the preheating combustion zone 212 and a small portion of the injected fuel gas start to be combusted in the mixed combustion zone 213, and further heat the combustion chamber 210, so that the temperature required for combustion of the high-temperature air in the high-temperature air combustion zone 211 is reached. Most of the mixed gas of the fuel gas and the air injected by the nozzle 100 fills the whole high-temperature air combustion area 211, and as the temperature of the high-temperature air combustion area 211 is higher than the self-ignition point of the fuel, high-temperature air combustion is formed, the fuel burns mildly, the flame frontal surface disappears, the temperature of the whole high-temperature combustion area is very uniform, the reaction rate in the combustion process is low, the local heat release is less, the heat flow distribution is uniform, the combustion peak temperature is low, and the noise is extremely low.
The present invention further provides a gas water heater, referring to fig. 6, the gas water heater includes a main body 20, a heat exchanger 30, a preheating burner 40 and a burner 10 (hereinafter, referred to as a high temperature air burner 10 for distinguishing from the preheating burner 40), the specific structure of the burner 10 refers to the above embodiments, a heat exchange chamber 21 and a smoke exhaust port 22 communicated with the heat exchange chamber 21 are disposed in the main body 20; the heat exchanger 30 is arranged in the heat exchange chamber 21; the burner 10 is mounted to the main body 20; the flue gas outlet of the burner 10 is communicated with the heat exchange chamber 21; the preheating burner 40 is installed at the main body 20, and the preheating burner 40 serves to deliver the mixture gas after ignition to the combustion chamber 210 of the burner 10 and preheat the combustion chamber 210 to a target temperature. Since the gas water heater adopts all the technical schemes of all the embodiments, the gas water heater at least has all the beneficial effects brought by the technical schemes of the embodiments. It can be appreciated that the gas water heater can effectively reduce CO and NOx emissions and reduce noise of the gas water heater due to the use of the burner 10 in the gas water heater.
It can be understood that, because the burner 10 is used in the gas water heater of the present invention, the embodiment of the gas water heater of the present invention includes all technical solutions of all embodiments of the burner 10, and the achieved technical effects are also completely the same, and are not described herein again. Wherein, the preheating burner 40 can automatically adjust the heat load according to the air quantity required by the high-temperature air combustion to achieve the effect of quickly preheating the air, and simultaneously ensure low CO and NOx emission in the whole combustion process.
The working principle of the burner 10 of the present invention applied to a gas water heater is explained in conjunction with the above-mentioned embodiment of the burner 10:
the water heater is started, the controller controls the gas switch valve to be opened, the fan is started, the gas switch valve of the pre-mixer and the fan provide the air and the gas which are mixed according to a certain proportion to the pre-mixing chamber of the main body 20, after the air and the gas are fully mixed, the mixed gas is provided to the preheating burner 40 through the fan, the ignition device is ignited, the combustion is started in the preheating combustion area 212 of the combustion chamber 210, the temperature measuring device measures whether the high-temperature air combustion area 211 reaches the target temperature, after the target temperature is reached, the mixed gas is distributed to the preheating burner 40 and the high-temperature air burner 10 according to the proportion, the preheating burner 40 keeps burning, high-temperature smoke is continuously generated, the mixed gas is conveyed to the nozzle 100 to be sprayed into the combustion chamber 210, a small part of the sprayed gas and the gas which is not burnt in the mixing combustion area 213, and a large part of the gas is sprayed to the high-temperature air combustion area 211, and the high-temperature flue gas is combined to form high-temperature air for combustion. Because the fuel gas is sprayed through the nozzle 100, a entrainment effect is formed in the combustion chamber 210, so that a spraying combustion area and a flue gas reflux area are formed in the high-temperature air combustion area 211, part of the flue gas is intensively circulated in the high-temperature air combustion area 211, the sprayed fuel gas and the air are fully diluted, a lower oxygen concentration is formed, the combustion reaction speed is reduced, a higher temperature in the high-temperature air combustion area 211 is maintained, the temperature is higher than the spontaneous combustion point of the fuel, and spontaneous combustion is realized. As such, the present embodiment satisfies the condition of high-temperature air combustion (mld combustion): high-temperature preheating air is matched with high-speed jet flow to realize entrainment of high-temperature flue gas and dilution of air jet flow, so that the oxygen concentration is lower than a certain value, and the temperature is higher than the self-ignition point of fuel. High-temperature flue gas generated by combustion enters the heat exchange chamber 21 through the flue gas outlet, is subjected to heat exchange through the heat exchanger 30 and then is discharged to the outside from the smoke outlet 22, so that hot water is prepared.
The above description is only an alternative embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (15)
1. A nozzle for a combustor, comprising:
a nozzle body having an injection inlet, an injection outlet, and an injection passage communicating the injection inlet and the injection outlet; and
and the rotational flow mechanism is arranged in the injection channel and is used for forming rotational flow of the airflow flowing through the injection channel and then spraying the airflow.
2. The nozzle of claim 1, wherein the swirling mechanism includes guide vanes provided to project from an inner wall surface of the injection passage.
3. The nozzle of claim 2, wherein the swirling mechanism comprises a plurality of guide vanes, the guide vanes are arranged at intervals along the circumferential direction of the injection passage, and the extending direction of each guide vane forms an included angle with the axis of the injection passage.
4. The nozzle of claim 3, wherein a plurality of the guide vanes are evenly arranged around a circumference of the injection passage.
5. The nozzle of claim 3, wherein the guide vanes are angled at an angle greater than or equal to 10 degrees and less than or equal to 60 degrees from the cross-section of the injection passage.
6. The nozzle according to claim 3, wherein a ratio of a height of the guide vane projecting from the inner wall surface of the injection passage to an inner diameter of the injection passage is greater than or equal to 0.05 and less than or equal to 0.5; and/or the ratio of the thickness of the guide vane to the height of the guide vane protruding out of the injection channel is greater than or equal to 0.1 and less than or equal to 1.
7. The nozzle according to claim 3, wherein the number n of guide vanes and the extension a of the guide vanes satisfy 0.5 x pi x D ≦ a x cos α x n ≦ 5 x pi x D, where D is the inner diameter of the injection passage and α is the angle of the guide vanes with the cross section of the injection passage.
8. A nozzle as claimed in any one of claims 2 to 7, wherein said guide vanes are provided at an end of said spray passage adjacent said spray outlet.
9. The nozzle of claim 2, wherein the guide vanes are swirl vanes, angled vanes, or helical vanes.
10. A burner, comprising:
a combustion body having a combustion chamber formed therein; and
the nozzle of any one of claims 1 to 9, having an injection outlet communicating with the combustion chamber and adapted to inject gas and/or air into the combustion chamber to cause high temperature air combustion to occur within the combustion chamber.
11. The burner of claim 10, wherein the combustion body is rectangular in cross-section and the burner includes a plurality of said nozzles spaced along the length of the combustion body.
12. The burner of claim 11, wherein a plurality of the nozzles are provided on both sides of the combustion body in the width direction, and the plurality of the nozzles on both sides of the combustion body in the width direction are staggered in the length direction of the combustion body.
13. The burner of claim 11, further comprising a gas distribution member mounted to an outer wall surface of the combustion body, the gas distribution member defining a gas distribution chamber, the plurality of nozzles having injection inlets in communication with the gas distribution chamber, the gas distribution chamber having gas inlets.
14. The burner of claim 10, wherein the combustion chamber comprises a high temperature air combustion zone, a mixed combustion zone and a preheating combustion zone which are sequentially arranged and communicated in a vertical direction, and the nozzle is communicated with the mixed combustion zone for injecting air and/or fuel gas to the mixed combustion zone and the high temperature air combustion zone.
15. A gas water heater, comprising:
the main body is internally provided with a heat exchange chamber and a smoke outlet communicated with the heat exchange chamber;
the heat exchanger is arranged in the heat exchange chamber;
a burner as claimed in any one of claims 10 to 14, mounted to the body, the flue gas outlet of the burner communicating with the heat exchange chamber; and
the preheating burner is mounted on the main body and used for conveying the ignited mixed gas to a combustion chamber of the burner and preheating the combustion chamber to a target temperature.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011073991.8A CN114353082A (en) | 2020-09-30 | 2020-09-30 | Nozzle, combustor and gas heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011073991.8A CN114353082A (en) | 2020-09-30 | 2020-09-30 | Nozzle, combustor and gas heater |
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| Publication Number | Publication Date |
|---|---|
| CN114353082A true CN114353082A (en) | 2022-04-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011073991.8A Withdrawn CN114353082A (en) | 2020-09-30 | 2020-09-30 | Nozzle, combustor and gas heater |
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| CN (1) | CN114353082A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030089801A1 (en) * | 2001-11-14 | 2003-05-15 | Mitsubishi Heavy Industries Ltd. | Combustor containing fuel nozzle |
| CN205939145U (en) * | 2016-08-26 | 2017-02-08 | 中能服能源科技股份有限公司 | Low NOx gas combustion ware structure |
| CN108800206A (en) * | 2018-06-06 | 2018-11-13 | 西北工业大学 | A kind of poor premix mould nozzle that fuel is sprayed from blade and loopful combustion chamber |
| US20190186749A1 (en) * | 2017-12-18 | 2019-06-20 | General Electric Company | Premixed pilot nozzle for gas turbine combustor |
| CN110822423A (en) * | 2019-10-08 | 2020-02-21 | 西安交通大学 | Multi-purpose burner with fins and different-diameter gas self-rotating premixing function |
| CN114110589A (en) * | 2020-08-31 | 2022-03-01 | 芜湖美的厨卫电器制造有限公司 | Nozzle, combustor and gas heater |
-
2020
- 2020-09-30 CN CN202011073991.8A patent/CN114353082A/en not_active Withdrawn
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030089801A1 (en) * | 2001-11-14 | 2003-05-15 | Mitsubishi Heavy Industries Ltd. | Combustor containing fuel nozzle |
| CN205939145U (en) * | 2016-08-26 | 2017-02-08 | 中能服能源科技股份有限公司 | Low NOx gas combustion ware structure |
| US20190186749A1 (en) * | 2017-12-18 | 2019-06-20 | General Electric Company | Premixed pilot nozzle for gas turbine combustor |
| CN108800206A (en) * | 2018-06-06 | 2018-11-13 | 西北工业大学 | A kind of poor premix mould nozzle that fuel is sprayed from blade and loopful combustion chamber |
| CN110822423A (en) * | 2019-10-08 | 2020-02-21 | 西安交通大学 | Multi-purpose burner with fins and different-diameter gas self-rotating premixing function |
| CN114110589A (en) * | 2020-08-31 | 2022-03-01 | 芜湖美的厨卫电器制造有限公司 | Nozzle, combustor and gas heater |
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Application publication date: 20220415 |