CN115013973B - Full premix water-cooling gas boiler - Google Patents
Full premix water-cooling gas boiler Download PDFInfo
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- CN115013973B CN115013973B CN202210620996.0A CN202210620996A CN115013973B CN 115013973 B CN115013973 B CN 115013973B CN 202210620996 A CN202210620996 A CN 202210620996A CN 115013973 B CN115013973 B CN 115013973B
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- water
- gas
- heat exchange
- exchange tube
- cooling
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- 239000000112 cooling gas Substances 0.000 title claims abstract description 9
- 238000001816 cooling Methods 0.000 claims abstract description 72
- 238000002485 combustion reaction Methods 0.000 claims abstract description 38
- 239000002737 fuel gas Substances 0.000 claims abstract description 17
- 239000007789 gas Substances 0.000 claims description 90
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 21
- 239000000779 smoke Substances 0.000 claims description 19
- 230000000694 effects Effects 0.000 claims description 12
- 238000007789 sealing Methods 0.000 claims description 7
- 238000002156 mixing Methods 0.000 claims description 6
- 239000011148 porous material Substances 0.000 claims description 6
- 238000011010 flushing procedure Methods 0.000 claims description 5
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 abstract description 12
- 239000003546 flue gas Substances 0.000 abstract description 12
- 238000013461 design Methods 0.000 abstract description 6
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 abstract description 4
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 238000004134 energy conservation Methods 0.000 abstract description 2
- 229910052757 nitrogen Inorganic materials 0.000 abstract description 2
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 9
- 238000010586 diagram Methods 0.000 description 4
- 238000005496 tempering Methods 0.000 description 4
- 230000002265 prevention Effects 0.000 description 3
- 238000012546 transfer Methods 0.000 description 3
- 239000000446 fuel Substances 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H8/00—Fluid heaters characterised by means for extracting latent heat from flue gases by means of condensation
- F24H8/006—Means for removing condensate from the heater
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
- F23D14/04—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone induction type, e.g. Bunsen burner
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/46—Details, e.g. noise reduction means
- F23D14/62—Mixing devices; Mixing tubes
- F23D14/64—Mixing devices; Mixing tubes with injectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/46—Details, e.g. noise reduction means
- F23D14/70—Baffles or like flow-disturbing devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/46—Details, e.g. noise reduction means
- F23D14/72—Safety devices, e.g. operative in case of failure of gas supply
- F23D14/78—Cooling burner parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H9/00—Details
- F24H9/0005—Details for water heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H9/00—Details
- F24H9/18—Arrangement or mounting of grates or heating means
- F24H9/1809—Arrangement or mounting of grates or heating means for water heaters
- F24H9/1832—Arrangement or mounting of combustion heating means, e.g. grates or burners
- F24H9/1836—Arrangement or mounting of combustion heating means, e.g. grates or burners using fluid fuel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D2203/00—Gaseous fuel burners
- F23D2203/007—Mixing tubes, air supply regulation
-
- 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
- Y02E20/30—Technologies for a more efficient combustion or heat usage
Abstract
The invention discloses a full premix water-cooling gas boiler, which comprises a mixer, wherein the mixer and a water-cooling burner are coaxially arranged at the axis position of the boiler, an outlet at the bottom of the mixer is communicated with an inlet of the water-cooling burner, and a water-cooling heat exchange tube bundle and a convection heat exchange tube bundle are sequentially arranged at the outer side of the water-cooling burner; the outer side of the mixer is annularly provided with an upper header, the outer side of the water-cooled burner at the lower part of the hearth is annularly provided with a lower header, and the upper header and the lower header are communicated by a water-cooled heat exchange tube bundle and a convection heat exchange tube bundle; the water-cooled burner is provided with a dew bearing plate below, a condensate discharge pipe is arranged below the dew bearing plate, a chimney is arranged between the dew bearing plate and the condensate discharge pipe, and a boiler bracket is used for supporting the whole device. The invention can realize full and uniform premixing of fuel gas and air, prevent backfire while burning with low nitrogen, and efficiently utilize the heat of flue gas, and the design of low-temperature combustion is also beneficial to the safe operation of the boiler while realizing energy conservation and emission reduction.
Description
Technical Field
The invention belongs to the technical field of gas boilers, and particularly relates to a full-premix water-cooling gas boiler.
Background
The pollutants produced by natural gas fuels are mainly nitrogen oxides, which are divided into three main categories: thermal NOx, fuel NOx and rapid NOx, nitrogen oxides generated by boiler combustion are mainly thermal NOx, and the main influencing factors of the nitrogen oxides are temperature, and the higher the combustion temperature is, the more thermal NOx is. Therefore, in order to develop low NOx gas burners to meet the latest environmental standards, the core is to reduce the gas temperature at the time of combustion. The traditional full premix burner is widely adopted because of uniform and stable combustion, but has the outstanding problem of being easier to generate thermal NOx because of high combustion strength and higher combustion temperature. In traditional boiler designs, heat carries mostly to one side of the water-cooled heat exchange tube bundle via flue gas, resulting in extremely uneven heat exchange and easy tube explosion accidents.
Disclosure of Invention
In order to overcome the technical problems, the invention aims to provide the full-premixing water-cooling gas boiler, which can realize full and uniform premixing of gas and air, prevent tempering while burning with low nitrogen, efficiently utilize the heat of flue gas, realize energy conservation and emission reduction, and simultaneously realize safe operation of the boiler by virtue of the design of low-temperature combustion.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
the full premix water-cooling gas boiler comprises a mixer 2, wherein the mixer 2 and a water-cooling burner 4 are coaxially arranged at the axis of the boiler, an outlet at the bottom of the mixer 2 is communicated with an inlet of the water-cooling burner 4, and a water-cooling heat exchange tube bundle 6a and a water-cooling heat exchange tube bundle 6b are sequentially arranged outside the water-cooling burner 4; the outside of the water-cooling heat exchange tube bundle 6b is outwards sequentially provided with a convection heat exchange tube bundle 5a and a convection heat exchange tube bundle 5b; the outer side of the mixer 2 is annularly provided with an upper header 3, the outer side of the water-cooled burner 4 at the lower part of the hearth is annularly provided with a lower header 7, and the upper header 3 and the lower header 7 are communicated by a water-cooled heat exchange tube bundle 6a and a water-cooled heat exchange tube bundle 6b, a convection heat exchange tube bundle 5a and a convection heat exchange tube bundle 5b; a dew bearing plate 9 is arranged below the water-cooled burner 4, a condensate discharge pipe 11 is arranged below the dew bearing plate, a chimney 8 is arranged between the dew bearing plate 9 and the condensate discharge pipe 11, and a boiler bracket 10 is used for supporting the whole device.
The water-cooled burner 4 comprises burner cooling pipes 43, the burner cooling pipes 43 are uniformly arranged along the circumferential direction, the upper end of each burner cooling pipe 43 is connected with a water-cooled burner upper header 42, and the lower end is connected with a water-cooled burner lower header 46; a water inlet pipe 41 is arranged on the upper side of the upper header 42 of the water-cooled burner and is connected with boiler feed water; the water-cooled burner lower header 46 is connected with the boiler lower header 7 by a communicating pipe 47.
The outer sides of the combustion head cooling pipes 43 of the water-cooled combustor 4 are provided with two circles of water-cooled heat exchange pipe bundles 6a and 6b in staggered arrangement along the circumferential direction; the outside of the water-cooling heat exchange tube bundle 6b is sequentially provided with a convection heat exchange tube bundle 5a and a convection heat exchange tube bundle 5b, and gaps are not reserved between adjacent tube bundles of the convection heat exchange tube bundle 5a and the convection heat exchange tube bundle 5b.
The outside of the combustion head cooling pipes 43 is welded with connected circular or spiral fins 44, the connected circular or spiral fins 44 form a diversion channel, the outside between the adjacent combustion head cooling pipes 43 is welded with an inward concave arc diversion sheet 45, the combustion head cooling pipes 43 are coaxially and annularly provided with the arc diversion sheet 45, the arc diversion sheet 45 and the adjacent two combustion head cooling pipes 43 respectively form a uniform section airflow channel 48, and the section of the airflow channel at the tail end of the water-cooled combustor 4 is sealed by adding a sealing end cover 49.
The mixer 2 comprises an air inner cylinder 21, an air outer cylinder 24 and a ring-shaped gas cylinder 23 which are sequentially arranged from inside to outside, a swirl vane 26 is arranged at the inlet of the air inner cylinder 21, a swirl vane 29 is arranged at the inlet of the air outer cylinder 24, a flow equalizing pore plate 28 is arranged at the initial position of the ring-shaped gas cylinder 23, a nozzle 210 is arranged on the inner wall of the ring-shaped gas cylinder 23, a nozzle 211 is arranged on the outer wall of the ring-shaped gas cylinder 23, and the inner wall nozzle 210 and the outer wall nozzle 211 are tangentially arranged in a boss mode in a ring shape.
The inner side of the swirl vane 26 in the air inner cylinder 21 is connected to the circular tube 27 at the axis, the outer side is connected to the inner wall of the air inner cylinder 21, the air flows through the swirl vane 26 and the swirl vane 29 to form swirl air, the fuel gas flows through the flow equalizing pore plate to be uniformly distributed, and then the fuel gas is respectively ejected inwards and outwards at a certain angle from the inner wall nozzle 210 and the outer wall nozzle 211 of the annular fuel gas cylinder and vertically opposite-flushing and mixing with the swirl air, so that the premixing effect is more uniform and sufficient.
The bottom of the air inner cylinder 21 is an air inner cylinder outlet 215, the outer side of the air inner cylinder outlet 215 is a circular-cone-shaped expanding wall surface, the included angle between the generatrix of the circular-cone-shaped wall surface and the axis can be determined according to specific dimensions, the wall surface is used as a constraint wall surface for expanding the air inner cylinder 21 and also plays a role in sealing the tail end of the circular-cone-shaped gas cylinder 23, so that the gas in the circular-cone-shaped gas cylinder has enough pressure to be ejected from the nozzle on the inner side wall surface and the outer side wall surface.
The mixer 2 is a petal-shaped grid in annular arrangement, and comprises 6 branch pipelines 34 arranged at each branch of the main gas pipeline 32, the main gas pipeline 32 penetrates through the outer wall of the air cylinder 31, bends at the axis of the air cylinder 31, stretches along the axis, seals the tail end 37 of the main gas pipeline, radially stretches out 6 branch pipelines 34 at equal positions, is communicated by a small-sized air outlet pipeline 35, is provided with air holes 36, the number of the air holes on each circle of pipelines is set in a proportional relation according to the distance from the air outlet pipeline 35 to the axis, so that the fuel gas on the same section is uniformly distributed, the air flow and the fuel gas flow are in opposite flushing arrangement, the mixing effect is more uniform, the air holes on each circle of pipelines are in opposite flushing arrangement according to the distance from the air outlet pipeline 35 to the axis, the air flow and the fuel gas flow are in opposite flushing arrangement, and the branch pipelines 34 can be in constant or stepwise tapered along the air flow direction.
The branch pipeline 34 adopts a reducing pipeline, namely, the diameter of the pipeline is gradually reduced along the airflow direction, so that the pressure of the gas in the gas outlet pipeline 35 with different distances from the axis on the same section is uniform, the gas flow difference of each gas hole 36 on the same section is reduced, and the isobaric gas supply is realized.
The water-cooled burner 4 has four arrangement forms, namely a straight tube type water-cooled burner of a light tube, a straight tube type water-cooled burner of a fin tube, a convergent water-cooled burner of the light tube and a convergent water-cooled burner of the fin tube.
The convection heat exchange tube bundles 5a and 5b are divided into a high-temperature convection tube bundle 5a and a low-temperature convection tube bundle 5b which are circumferentially arranged, the outer sides of the single convection heat exchange tube bundles are water tubes 51, smoke tubes 52 are sleeved in the water tubes, spiral guide vanes 53 are arranged in the smoke tubes, the lower sides of the smoke tubes are smoke inlets, and the upper sides of the smoke tubes are smoke outlets.
The water-cooling heat exchange tube bundles 6a and 6b are coaxially and circumferentially distributed on the outer side of the water-cooling burner 4, the inner water-cooling heat exchange tube bundles 6a and the outer water-cooling heat exchange tube bundles 6b are arranged in staggered mode, the number is the same, and the distance between the outer tube bundles is larger than that between the outer tube bundles.
The invention has the beneficial effects that:
the air flows through the swirl blades at the inlets of the air inner cylinder and the air outer cylinder to form swirl air, the fuel gas flows through the flow equalizing pore plate to be uniformly distributed, and then is respectively ejected inwards and outwards at a certain angle from the inner wall nozzle and the outer wall nozzle of the annular fuel gas cylinder, and is vertically opposite-punched and mixed with the swirl air, so that the premixing effect is more uniform and sufficient.
The inner wall nozzle and the outer wall nozzle of the annular gas cylinder are arranged in an annular tangential mode in a boss mode to form rotational flow gas, so that the mixing effect of the rotational flow gas and rotational flow air is enhanced.
The outside of the air inner cylinder outlet is a ring-shaped gas cylinder rear end cover which is an expanded truncated cone-shaped wall surface, and the included angle between the generatrix of the truncated cone-shaped wall surface and the axis can be determined according to specific dimensions, and the generatrix should pass through the circumferential edge line of the inlet of the water-cooled burner along the extension line of the generatrix. The wall surface not only serves as a constraint wall surface for expanding the gas in the air inner cylinder, but also plays a role in closing the tail end of the annular gas cylinder, so that the gas in the annular gas cylinder has enough pressure to be ejected from the inner and outer wall surface nozzles.
The branch pipelines are communicated by a small-sized air outlet pipeline. The gas outlet pipelines are provided with gas holes, and the number of the gas holes on each circle of pipelines is set in a proportional relationship according to the distance from the gas outlet pipeline to the axle center, so that the gas on the same section can be uniformly distributed. The air flow and the gas flow are arranged in opposite impact, so that the mixing effect is more uniform.
The branch pipe can have another design scheme adopting a reducing pipe, namely the diameter of the pipe gradually reduces along the air flow direction. The pressure of the gas in the gas outlet pipeline with different distances from the axis on the same section can be uniform, the gas flow difference of each gas hole on the same section is reduced, and the isobaric gas supply is realized.
The outside of the cooling pipe of the combustion head is welded with circular or spiral fins which are connected, so that the heat exchange area is increased, the combustion temperature is effectively reduced, and the generation amount of thermal NOx is reduced. The connected fins form a diversion channel, so that the mixed gas can realize the ignition combustion of uniformly dispersed small flames before combustion, and the concentrated high-temperature combustion is avoided. An inward concave arc-shaped guide vane is welded on the outer side between two adjacent combustion head cooling pipes, and the arc-shaped guide vane and two adjacent combustion head cooling pipes form a uniform-section airflow channel respectively, so that the purpose of tempering prevention is achieved. Meanwhile, the outlet section is smaller, and the flow channel is bent during air flow return, so that the flow path is longer than that of the direct current channel, and the tempering prevention effect is further enhanced. The air flow passage section at the tail end of the water-cooled burner is covered and sealed, and the sealing end cover ensures that the mixed gas can be sprayed to the periphery along the radial direction under enough pressure.
The inner water-cooling heat exchange tube bundles and the outer water-cooling heat exchange tube bundles are arranged in staggered mode, the number of the outer water-cooling heat exchange tube bundles is the same, the distance between the outer water-cooling heat exchange tube bundles is larger than that of the inner water-cooling heat exchange tube bundles, heat absorption of water in the water-cooling heat exchange tube bundles is enhanced, combustion temperature is further reduced, and reduction of thermal NOx is facilitated. Meanwhile, the water-cooling heat exchange tube bundles can also be arranged in a tapered mode.
The outside of the single convection heat exchange tube bundle is a water tube, a smoke tube is sleeved in the water tube, a spiral guide vane is arranged in the smoke tube, the lower side is a smoke inlet, and the upper side is a smoke outlet. The heat transfer can be enhanced by convection of the flue gas and water, and the heat of the flue gas is effectively utilized.
Drawings
FIG. 1 is a schematic view of the boiler according to the present invention.
Fig. 2 is a top view and a cross-sectional view of a swirl-counter-flow mixer.
Fig. 3a is a schematic diagram of a counter-impact mixer.
Fig. 3b is a schematic diagram of a tapered pipe diameter counter-impingement mixer.
FIGS. 4a-I are schematic diagrams of a fin tube straight barrel type water-cooled burner.
FIGS. 4a-II are schematic diagrams of a fin tube tapered water cooled burner.
FIG. 4b-I is a schematic illustration of a straight tube water cooled burner with a light pipe.
FIGS. 4b-II are schematic illustrations of a light pipe tapered water cooled burner.
Fig. 5 is a schematic view of a bundle of convective heat transfer tubes.
FIG. 6 is a schematic view of a circumferential arrangement of a water cooled burner head, a cooling heat exchanger tube bundle, and a convection heat exchanger tube bundle.
Detailed Description
The invention is described in further detail below with reference to the accompanying drawings.
As shown in fig. 1-6: a full premix water-cooling gas boiler comprises a mixer 2, a water-cooling burner 4, a water-cooling heat exchange tube bundle 6a, a water-cooling heat exchange tube bundle 6b, a convection heat exchange tube bundle 5a, a convection heat exchange tube bundle 5b, an upper header 3, a lower header 7, a furnace wall 1, a chimney 8, a dew bearing plate 9, a boiler bracket 10 and a condensate discharge pipe 11; the mixer 2 and the water-cooled burner 4 are coaxially arranged at the axis position of the boiler, an outlet at the bottom of the mixer 2 is communicated with an inlet of the water-cooled burner 4, and a water-cooled heat exchange tube bundle 6a and a water-cooled heat exchange tube bundle 6b are arranged outside the water-cooled burner 4; the outside of the water-cooling heat exchange tube bundle 6b is sequentially provided with a convection heat exchange tube bundle 5a and a convection heat exchange tube bundle 5b. The outer side of the mixer 2 is annularly provided with an upper header 3, the outer side of the water-cooled burner 4 at the lower part of the hearth is annularly provided with a lower header 7, and the upper header 4 and the lower header 7 are communicated with each other by water-cooled heat exchange tube bundles 6a and 6b and convection heat exchange tube bundles 5a and 5b; a dew bearing plate 9 is arranged below the water-cooled burner 4, a condensate discharge pipe 11 is arranged below the dew bearing plate, a chimney 8 is arranged between the dew bearing plate 9 and the condensate discharge pipe 11, and a boiler bracket 10 is used for supporting the whole device.
In the mixer (fig. 2), air flows through the swirl blades 26 and 29 at the inlets of the air inner cylinder 21 and the air outer cylinder 24 to form swirl air, and fuel gas enters from the fuel gas inlet pipeline 25 and then passes through the flow equalizing pore plate 28 to be uniformly distributed on the annular section, and then is respectively emitted inwards and outwards at a certain angle from the inner wall nozzle 210 and the outer wall nozzle 211 of the annular fuel gas cylinder 23 and vertically and oppositely-punched and mixed with the swirl air, so that the premixing effect is more uniform.
The second design of the mixer provided in the present invention (fig. 3 a) operates in the following manner: the fuel gas enters from the main pipe 32, passes through the branch pipe 34, and exits from the air hole 36 of the small air outlet pipe 35. Air enters from the air cylinder 31, and air flow and gas flow are mixed in an opposite way and then continue to flow forwards, and the opposite way can enable the mixing effect to be more uniform. Because the number of the air holes on each circle of the pipeline is arranged in a proportional relation according to the distance from the air outlet pipeline 35 to the axis, small fuel gas on the same section can be uniformly distributed in a punctiform way.
The branch pipe 34 is designed in an optimized way (fig. 3 b) based on the scheme, and the diameter of the branch pipe is gradually reduced along the air flow direction. When the gas is split from the main pipeline 32 to the gas outlet pipeline 35 through the branch pipeline 34, the gas pressure in the gas outlet pipeline 35 with different distances from the axis on the same section can be uniform, the gas flow difference of each gas hole 36 on the same section is reduced, and the isobaric gas supply is realized.
The mixed gas enters the water-cooled burner (fig. 4 a), and the cross section of the air flow passage at the tail end of the water-cooled burner is provided with a sealing end cover 49, so that the mixed gas can be sprayed from the gap diversion passage 48 of the cooling pipe of the adjacent burner head in a radial direction and around under enough pressure. The mixed gas is uniformly dispersed before combustion under the division action of the fins 44, so that the combustion can be more sufficient. Meanwhile, the concentrated high-temperature combustion of large flames is prevented, the small flame combustion is realized, and the combustion temperature and the generation of NOx are further reduced.
Further, when the mixed gas flows out in the water-cooled burner, the heat exchange area is increased because the round or spiral fins 44 are welded on the outer side of the cooling tube 43 of the burner, so that the combustion temperature is effectively reduced, and the purpose of reducing thermal NOx is achieved.
Further, the outer side of the circular or spiral fin 44 of the cooling tube 43 is provided with an arc-shaped flow deflector 45, so that the outlet section 48 is reduced, the gas flow rate is increased, and the purpose of preventing backfire can be achieved. Meanwhile, the outlet section is smaller, and the flow channel is bent during air flow return, so that the flow channel is longer than the flow channel, and the tempering prevention effect is further achieved.
There are four designs of water-cooled burner 4 that can be referred to: one is a straight tube type water-cooled burner (fig. 4 b-i) with simple structure, convenient processing and material saving, which can be used in low-capacity boilers; one is a straight tube type water-cooled burner (fig. 4 a-i), when the capacity of the boiler is increased, the fins play a role in dividing to prevent the concentrated high-temperature combustion of large flame, realize the combustion of small flame, further reduce combustion temperature and NOx generation; the other two are respectively a light pipe convergent water-cooled burner (fig. 4 b-ii) and a finned tube convergent water-cooled burner (fig. 4 a-ii), because the sealing end cover 49 is arranged at the air flow passage section at the tail end of the water-cooled burner, the cooling tube 43 of the combustion head is inclined inwards to form a truncated cone shape, so that the mixed gas can be sprayed out along the radial direction and the surrounding direction with enough pressure, and meanwhile, the mixed gas on each section along the central axis direction of the water-cooled burner realizes equal pressure and equal flow distribution, the uniform combustion prevents local high temperature and reduces the generation of NOx.
Further, after the mixed gas is ignited by the ignition gun, the formed flue gas firstly passes through the inner side cooling heat exchange tube bundle 6a to exchange heat with water in the tubes, and then passes through the outer side cooling heat exchange tube bundle 6b, so that the heat exchange effect is improved, the combustion temperature is reduced, and the generation of thermal NOx is further reduced due to the staggered arrangement of the inner side cooling heat exchange tube bundle and the outer side cooling heat exchange tube bundle.
Further, as shown in fig. 5 and 6, since there is no gap between adjacent single tubes of the heat convection tube bundle, the flue gas is concentrated downward, enters from the lower part of the flue tube 52 of the high temperature heat convection tube bundle 5a, flows upward spirally from the inside of the flue tube under the action of the spiral guide vane 53, exchanges heat with the water flowing downward in the water pipe 51 outside the flue tube 52, and flows out from the outlet at the upper part of the flue tube. The outflow is blocked by the low-temperature convection tube bundle 5b to flow downwards, then enters from the lower part of the low-temperature convection tube bundle 5b, and the process is repeated once. The flue gas from the upper part of the low-temperature convection tube bundle flows downwards to the dew bearing plate 9 along the inner wall 17 of the furnace wall and is discharged through the chimney 8. The flue gas passing through the convection heat exchange tube bundle can greatly improve the heat exchange effect with water, and the purpose of effectively utilizing the waste heat of the flue gas is achieved.
For the single convection heat exchange tube bundle shown in fig. 5, the outer side is a water tube 51, a smoke tube 52 is sleeved in the water tube, a spiral guide vane 53 is arranged in the smoke tube, the lower side is a smoke inlet, and the upper side is a smoke outlet. The heat transfer can be enhanced by convection of the flue gas and water, and the heat of the flue gas is effectively utilized.
The above is only for illustrating the technical idea of the present invention, and the protection scope of the present invention is not limited by this, and any modification made on the basis of the technical scheme according to the technical idea of the present invention, such as changing the opposite impact structure and angle of the mixer, and the smoke tube using the internal threaded tube instead of the spiral guide vane, etc., all fall within the protection scope of the claims of the present invention.
Claims (7)
1. The full-premix water-cooling gas boiler is characterized by comprising a mixer (2), wherein the mixer (2) and a water-cooling burner (4) are coaxially arranged at the axis of the boiler, an outlet at the bottom of the mixer (2) is communicated with an inlet of the water-cooling burner (4), and a water-cooling heat exchange tube bundle (6 a) and a water-cooling heat exchange tube bundle (6 b) are sequentially arranged outside the water-cooling burner (4); the water-cooling heat exchange tube bundles (6 a) and the water-cooling heat exchange tube bundles (6 b) are sequentially arranged on the outer sides of the convection heat exchange tube bundles (5 a) and the convection heat exchange tube bundles (5 b), an upper header (3) is annularly arranged on the outer sides of the mixers (2), a lower header (7) is annularly arranged on the outer sides of the water-cooling burners (4) at the lower part of the hearth, and the upper header (3) and the lower header (7) are communicated with each other through the water-cooling heat exchange tube bundles (6 a), the water-cooling heat exchange tube bundles (6 b), the convection heat exchange tube bundles (5 a) and the convection heat exchange tube bundles (5 b); a dew bearing disc (9) is arranged below the water-cooled burner (4), a condensate discharge pipe (11) is arranged below the dew bearing disc, a chimney (8) is arranged between the dew bearing disc (9) and the condensate discharge pipe (11), and a boiler bracket (10) is used for supporting the whole device;
the mixer (2) comprises an air inner cylinder (21), an air outer cylinder (24) and a circular gas cylinder (23) which are sequentially arranged from inside to outside, a swirl vane (26) is arranged at the inlet of the air inner cylinder (21), a swirl vane (29) is arranged at the inlet of the air outer cylinder (24), a flow equalizing pore plate (28) is arranged at the initial position of the circular gas cylinder (23), a nozzle (210) is arranged on the inner wall of the circular gas cylinder (23), a nozzle (211) is arranged on the outer wall of the circular gas cylinder (23), and the nozzle (210) on the inner wall of the circular gas cylinder (23) and the nozzle (211) on the outer wall of the circular gas cylinder are tangentially arranged in a boss mode in a circular mode;
the inner side of a swirl vane (26) in the air inner cylinder (21) is connected to a circular tube (27) at the axis, the outer side of the swirl vane is connected to the inner wall of the air inner cylinder (21), swirl wind is formed after air flows through the swirl vane (26) and the swirl vane (29), fuel gas flows through a flow equalizing pore plate and is uniformly distributed, and then the fuel gas is respectively ejected inwards and outwards at a certain angle from an inner wall nozzle (210) and an outer wall nozzle (211) of the annular fuel gas cylinder and vertically opposite-flushing and mixing with swirl air, so that the premixing effect is more uniform and sufficient;
the bottom of the air inner cylinder (21) is an air inner cylinder outlet (215), the outer side of the air inner cylinder outlet (215) is a circular truncated cone-shaped wall surface which expands, and the wall surface not only serves as a constraint wall surface for expanding the air of the air inner cylinder (21), but also plays a role in closing the tail end of the circular gas cylinder (23), so that the gas in the circular gas cylinder has enough pressure to be ejected from the nozzle on the inner side wall surface and the outer side wall surface.
2. The full premix water-cooled gas boiler as recited in claim 1, wherein the water-cooled burner (4) comprises burner cooling pipes (43), the burner cooling pipes (43) are circumferentially and uniformly arranged, the upper end of the burner cooling pipes (43) is connected with a water-cooled burner upper header (42), and the lower end is connected with a water-cooled burner lower header (46); the outside of the combustion head cooling pipe (43) is provided with a water-cooling heat exchange pipe bundle (6 a) and a water-cooling heat exchange pipe bundle (6 b) which are staggered along the circumferential direction; the outside of the water-cooling heat exchange tube bundle (6 b) is sequentially circumferentially provided with a convection heat exchange tube bundle (5 a) and a convection heat exchange tube bundle (5 b), and gaps are not reserved between adjacent tube bundles of the convection heat exchange tube bundle (5 a) and the convection heat exchange tube bundle (5 b).
3. The full premix water-cooled gas boiler of claim 2, wherein circular or spiral fins (44) connected are welded on the outer side of each combustion head cooling pipe (43), the connected circular or spiral fins (44) form a diversion channel, inward concave arc diversion sheets (45) are welded on the outer side between adjacent combustion head cooling pipes (43), the arc diversion sheets (45) are coaxially and annularly arranged on the combustion head cooling pipes (43), the arc diversion sheets (45) and the two adjacent combustion head cooling pipes (43) form a uniform-section airflow channel (48) respectively, and a sealing end cover (49) is added at the airflow channel section of the tail end of the water-cooled combustor (4) for sealing.
4. The full premix water-cooling gas boiler according to claim 1, wherein the mixer (2) is a petal-shaped grid arranged in a ring shape, and comprises 6 branch pipelines (34) arranged at each branch of the gas main pipeline (32), the gas main pipeline (32) passes through the outer wall of the air cylinder (31), is bent at the axis of the air cylinder (31), extends along the axis, the tail end (37) of the gas main pipeline is sealed, 6 branch pipelines (34) radially extend out at equal positions, the branch pipelines are communicated by a small gas outlet pipeline (35), the gas outlet pipelines are provided with gas holes (36), the number of the gas holes on each circle of pipelines is arranged in a proportional relation with the distance from the gas outlet pipeline (35) to the axis, so that the gas on the same section can be uniformly distributed, the air flow and the gas flow are arranged in opposite to each other, the gas outlet pipeline (35) is provided with gas holes (36), the number of the gas holes on each circle of pipelines is arranged in a proportional relation with the distance from the gas outlet pipeline (35) to the axis, and the diameter of the branch pipelines can be constant or gradually reduced along the gas flow direction.
5. The full premix water-cooled gas boiler as recited in claim 4, wherein the branch pipeline (34) is a reducing pipeline, i.e. the diameter of the pipeline is gradually reduced along the air flow direction, so that the gas pressure in the gas outlet pipelines (35) with different distances from the axis on the same section can be uniform, the gas flow difference of each gas hole (36) on the same section is reduced, and the isobaric gas supply is realized.
6. The full premix water-cooled gas boiler as recited in claim 1, wherein the water-cooled burner (4) has four arrangements, which are respectively a straight tube type water-cooled burner with a light tube, a straight tube type water-cooled burner with a fin tube, a tapered water-cooled burner with a light tube and a tapered water-cooled burner with a fin tube.
7. The full premix water-cooled gas boiler as claimed in claim 1, wherein the convection heat exchange tube bundle (5 a) and the convection heat exchange tube bundle (5 b) are divided into a high-temperature convection tube bundle (5 a) and a low-temperature convection tube bundle (5 b) which are circumferentially arranged, the outer side of the single convection heat exchange tube bundle is a water tube (51), a smoke tube (52) is sleeved in the water tube, a spiral guide vane (53) is arranged in the smoke tube, the lower side is a smoke inlet, and the upper side is a smoke outlet;
the water-cooling heat exchange tube bundles (6 a) and the water-cooling heat exchange tube bundles (6 b) are coaxially and circumferentially distributed on the outer side of the water-cooling combustor (4), the inner side water-cooling heat exchange tube bundles (6 a) and the outer side water-cooling heat exchange tube bundles (6 b) are arranged in a staggered mode, the number is the same, and the distance between the outer side tube bundles is larger than that between the outer side tube bundles.
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| CN202210620996.0A CN115013973B (en) | 2022-06-02 | 2022-06-02 | Full premix water-cooling gas boiler |
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| CN202210620996.0A CN115013973B (en) | 2022-06-02 | 2022-06-02 | Full premix water-cooling gas boiler |
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| CN115013973B true CN115013973B (en) | 2023-10-24 |
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| CN117128511B (en) * | 2023-10-27 | 2024-02-06 | 广东万和新电气股份有限公司 | Combustion device and full premix combustor |
Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03199805A (en) * | 1989-12-27 | 1991-08-30 | Hitachi Ltd | Low nox and burner for boiler |
| GB9212372D0 (en) * | 1991-06-11 | 1992-07-22 | Burco Dean Appliances Ltd | A gas fired boiler |
| JPH11287409A (en) * | 1998-03-31 | 1999-10-19 | Miura Co Ltd | Low nox burner |
| EP3135997A1 (en) * | 2015-08-31 | 2017-03-01 | Riello S.p.A. | Air/gas mixing apparatus for premix burners and premix burner provided with such an apparatus |
| CN107218602A (en) * | 2017-07-19 | 2017-09-29 | 上海华之邦科技股份有限公司 | A kind of low heat value/low-pressure gas burner |
| CN109323253A (en) * | 2018-09-07 | 2019-02-12 | 西安交通大学 | One kind uniformly premixing low NOx gas burner |
| CN110631260A (en) * | 2019-10-14 | 2019-12-31 | 西安交通大学 | Cylindrical slit type full-premixing water-cooled combustion head |
| CN111141028A (en) * | 2020-01-13 | 2020-05-12 | 西安交通大学 | Gas condensing boiler with high-adjusting-ratio water-cooling premixed combustion and high-strength heat exchange |
| CN112460567A (en) * | 2020-11-23 | 2021-03-09 | 西安交通大学 | Gas boiler with concentric single pipe ring water-cooling combustion and heat exchange |
| CN112460568A (en) * | 2020-11-23 | 2021-03-09 | 西安交通大学 | Full premix water-cooling gas boiler of U-shaped tubular structure |
| CN112555828A (en) * | 2020-12-15 | 2021-03-26 | 西安交通大学 | Hearth and combustor cooling type surface cold flame premixing gas boiler |
| WO2021244494A1 (en) * | 2019-10-17 | 2021-12-09 | 芜湖美的厨卫电器制造有限公司 | Combustor and gas water heater |
| CN114353072A (en) * | 2020-09-30 | 2022-04-15 | 芜湖美的厨卫电器制造有限公司 | Combustor and water heater |
-
2022
- 2022-06-02 CN CN202210620996.0A patent/CN115013973B/en active Active
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03199805A (en) * | 1989-12-27 | 1991-08-30 | Hitachi Ltd | Low nox and burner for boiler |
| GB9212372D0 (en) * | 1991-06-11 | 1992-07-22 | Burco Dean Appliances Ltd | A gas fired boiler |
| GB2256701A (en) * | 1991-06-11 | 1992-12-16 | Burco Dean Appliances Ltd | Gas fired boiler |
| JPH11287409A (en) * | 1998-03-31 | 1999-10-19 | Miura Co Ltd | Low nox burner |
| EP3135997A1 (en) * | 2015-08-31 | 2017-03-01 | Riello S.p.A. | Air/gas mixing apparatus for premix burners and premix burner provided with such an apparatus |
| CN107218602A (en) * | 2017-07-19 | 2017-09-29 | 上海华之邦科技股份有限公司 | A kind of low heat value/low-pressure gas burner |
| CN109323253A (en) * | 2018-09-07 | 2019-02-12 | 西安交通大学 | One kind uniformly premixing low NOx gas burner |
| CN110631260A (en) * | 2019-10-14 | 2019-12-31 | 西安交通大学 | Cylindrical slit type full-premixing water-cooled combustion head |
| WO2021244494A1 (en) * | 2019-10-17 | 2021-12-09 | 芜湖美的厨卫电器制造有限公司 | Combustor and gas water heater |
| CN111141028A (en) * | 2020-01-13 | 2020-05-12 | 西安交通大学 | Gas condensing boiler with high-adjusting-ratio water-cooling premixed combustion and high-strength heat exchange |
| CN114353072A (en) * | 2020-09-30 | 2022-04-15 | 芜湖美的厨卫电器制造有限公司 | Combustor and water heater |
| CN112460567A (en) * | 2020-11-23 | 2021-03-09 | 西安交通大学 | Gas boiler with concentric single pipe ring water-cooling combustion and heat exchange |
| CN112460568A (en) * | 2020-11-23 | 2021-03-09 | 西安交通大学 | Full premix water-cooling gas boiler of U-shaped tubular structure |
| CN112555828A (en) * | 2020-12-15 | 2021-03-26 | 西安交通大学 | Hearth and combustor cooling type surface cold flame premixing gas boiler |
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