WO2015103754A1 - 一种多腔燃气空气混合装置 - Google Patents

一种多腔燃气空气混合装置 Download PDF

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Publication number
WO2015103754A1
WO2015103754A1 PCT/CN2014/070374 CN2014070374W WO2015103754A1 WO 2015103754 A1 WO2015103754 A1 WO 2015103754A1 CN 2014070374 W CN2014070374 W CN 2014070374W WO 2015103754 A1 WO2015103754 A1 WO 2015103754A1
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WIPO (PCT)
Prior art keywords
gas
air
mixing
chamber
pipe
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PCT/CN2014/070374
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English (en)
French (fr)
Inventor
张世萍
毕大岩
韦瑞洪
Original Assignee
艾欧史密斯(中国)热水器有限公司
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Application filed by 艾欧史密斯(中国)热水器有限公司 filed Critical 艾欧史密斯(中国)热水器有限公司
Priority to US15/110,377 priority Critical patent/US10823400B2/en
Priority to PCT/CN2014/070374 priority patent/WO2015103754A1/zh
Publication of WO2015103754A1 publication Critical patent/WO2015103754A1/zh

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Classifications

    • 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
    • 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
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/007—Mixing tubes, air supply regulation

Definitions

  • the invention relates to a multi-chamber gas-air mixing device applied to a full premixed combustion gas water heater, in particular to a mixer capable of realizing a segmented combustion function, belonging to the technical field of water heaters. Background technique
  • a fully premixed combustion system is a system in which gas and air are uniformly mixed once and then burned. It is characterized by: having a small excess air ratio (ie, the ratio of the actual required air volume to the theoretical required air volume, generally less than 1.5), lower pollutant (N0x, CO) emissions, high combustion intensity, The flame is short, the burning area is large, the combustion load is small, and the combustion noise is small.
  • a small excess air ratio ie, the ratio of the actual required air volume to the theoretical required air volume, generally less than 1.5
  • pollutant N0x, CO
  • the flame is short, the burning area is large, the combustion load is small, and the combustion noise is small.
  • the application of full premixed combustion systems has a certain history, and with the improvement of various performance requirements, especially the state's control of pollutant emissions is becoming more and more strict, its development prospects are more optimistic.
  • Full premixed burners differ greatly from common premixed burners in that they are typically ceramic, stainless steel, carbon fiber, and iron-chromium-aluminum wire mesh. It is characterized in that it can burn very well at a small excess air ratio; at the same time, the flame temperature is about 30 CTC higher than the temperature of the partial premixed combustion due to less air for combustion. Higher flue gas temperatures and less flue gas (excess air ratio) greatly increase heat transfer efficiency and tend to produce condensate, so full premixed combustion is often used in condensing combustion systems.
  • the probability of condensate generation is determined by the excess air coefficient of the system and the input load: 1) When the input load changes linearly within a certain range, the smaller the load, the larger the relative heat exchange area, the higher the heat exchange efficiency, the higher the probability of generating condensed water. For a certain combustion system, when the excess air coefficient is constant, If the input load is small enough, condensation will inevitably occur. 2) The excess air ratio is directly related to the generation of condensed water. In general, the dew point temperature Td is an important parameter to measure whether condensate will be generated.
  • the flue gas dew point is proportional to the flue gas moisture content (ds), and the flue gas is wet.
  • the amount is equal to the ratio of the water vapor quality in the flue gas to the total flue gas mass.
  • the larger the excess air coefficient the greater the total flue gas mass, the lower the flue gas moisture content, the lower the flue gas dew point temperature, and the lower the probability of producing condensed water. Therefore, for non-condensing products, it is necessary to start from these two aspects to avoid condensation.
  • the combustion system is mostly composed of several independent burners. By controlling the start and stop of some burners, the adjustment between the maximum and minimum loads can be completed, as shown in Figure 1.
  • the excess air coefficient is generally about 2; at the minimum load, only part of the burner works, and the other part of the burner only passes through the air, and the excess air coefficient can reach 10 or more. This system is very unlikely to produce condensate.
  • the excess air ratio is maintained at about 1.5 over the entire load range. If it is too high, it will leave the flame, and if it is too low, it will be extinguished or tempered, which will cause condensed water to appear under small load. The probability is greatly increased. According to the experimental results, for a given heat exchange system, the condensed water may only decrease when the excess air ratio exceeds 2. Therefore, how to apply the full premixed combustion system to the non-condensing product without the risk of condensed water is one of the problems to be solved by the present invention.
  • a Chinese patent application number is 200310101740, the invention name is "gas burner capable of multi-stage control", and discloses a gas burner capable of multi-stage control, the burner being composed of a plurality of independent tubular burners.
  • a gas mixture supply device is further disposed in each of the separate tubular burners, and a venturi (venturi) and a manifold are disposed outside the mixed gas supply device to control the supply and mixing of the gas and the air, respectively.
  • the invention can solve the problem of segmentation, the structure is complicated, the volume is large, the manufacturing and assembly processes are required to be high, and the cost is correspondingly high.
  • the present invention provides a multi-chamber gas-air mixing device comprising at least two mixing chambers, each of which has an air inlet and a mixed gas outlet communicating with the burner, each of the mixing chambers respectively A gas pipeline is built in, and a gas nozzle is opened on each of the gas pipelines, and the gas nozzle has an orientation that intersects with a flow direction of air entering the mixing chamber.
  • a multi-chamber gas-air mixing device as described above, wherein at least two gas conduits within said mixing chamber are in communication, said interconnecting gas conduits comprising at least one control switching conduit.
  • the multi-chamber gas-air mixing device as described above, wherein the connected gas pipe further comprises at least one normally open pipe, the normally open pipe being connected with a gas transmission pipe of the peripheral, in the control switch pipe and A gas on-off valve for controlling opening and closing of the control switch pipe is disposed between the normally open pipes.
  • the multi-chamber gas-air mixing device as described above, wherein the gas-on-off valve is a solenoid valve, and a sealing member of the solenoid valve is movably blocked between the control switch pipe and the normally open pipe.
  • the multi-chamber gas-air mixing device as described above, wherein the gas pipe is vertically disposed on an air flow path of the mixing chamber.
  • the multi-chamber gas-air mixing device as described above, wherein the mixing chamber has a venturi type, and the venturi-type mixing chamber has a tapered throat section and a divergent mixing section.
  • the multi-chamber gas-air mixing device as described above, wherein the at least two mixing chambers are arranged side by side, and the two adjacent mixing chambers are separated by a partition, and the gas pipeline is opened through the partition
  • the mounting hole is disposed through the mixing chamber.
  • the multi-chamber gas-air mixing device as described above, wherein a uniform wind structure is provided at an upper portion of the mixing chamber.
  • the present invention has the following features and advantages:
  • the invention effectively segments the gas-air mixer through a plurality of mixing chambers, realizes a large load regulation ratio, and does not generate condensed water in each load section, thereby improving system reliability and life.
  • the built-in gas passage of the invention not only realizes the active control of controlling the fuel of the switch pipeline, but also reduces the volume of the mixer and greatly reduces the cost.
  • the orientation of the gas vent of the present invention intersects with the flow of air entering the mixing chamber to allow the gas to be thoroughly mixed with the air.
  • the present invention solves the problem that the conventional full premixed combustion system cannot be segmented compared with the prior art, and adopts a structure in which the gas passage is built in the mixer, and the fuel of the control switch is effectively controlled by the gas on/off valve.
  • Figure 1 is a characteristic diagram of a conventional partial premixed staged combustion
  • FIG. 2 is a schematic perspective view showing the first embodiment of the multi-chamber gas-air mixing device of the present invention
  • Figure 3 is a schematic view showing the structure of the A-A section of Figure 2;
  • Figure 4 is a schematic view showing the structure of the B-B section of Figure 3;
  • FIG. 5 is a schematic structural view of a second embodiment of the multi-chamber gas-air mixing device of the present invention.
  • the invention provides a multi-chamber gas-air mixing device, comprising at least two mixing chambers, each of which has an air inlet and a mixed gas outlet connected to the burner, and each of the mixing chambers is internally provided with a gas pipeline to reduce The overall volume of the mixing device.
  • a gas nozzle is opened on each gas pipe, and the direction of the gas nozzle intersects with the flow direction of the air entering the mixing chamber. In this way, the air and the gas are thoroughly mixed in the mixing chamber.
  • FIG. 2 is a schematic perspective view of a first embodiment of a multi-chamber gas-air mixing device according to the present invention
  • FIG. 3 is a schematic structural view of the AA cross-section of FIG. 2;
  • the multi-chamber gas-air mixing device of the present invention comprises: a first mixing chamber 1, a second mixing chamber 2, a first air inlet 11, a second air inlet 21, a first gas conduit 12, a second gas conduit 22, a gas on-off valve 5.
  • Mixed gas outlet (not shown).
  • the first mixing chamber 1 and the second mixing chamber 2 respectively have air inlets 11, 21 and a mixed gas outlet, and the air inlets 11, 21 are connected to the atmosphere, and air is supplied through the fan so that the outside air enters the mixing chambers 1, 2 and is mixed.
  • the air passage formed by the inner cavity of the cavity flows.
  • the mixed gas outlet is connected to the burner to provide mixed gas to the mixing chamber.
  • the first mixing chamber 1 has a first gas pipe 12 built therein, and one end of the first gas pipe 12 is connected to the gas conveying pipe and the gas regulating valve, and the direction of the arrow in FIG. 3 is the gas input direction.
  • the amount of gas introduced into the first gas pipe 12 is controlled by a gas regulating valve, and the other end of the first gas pipe 12 is connected to the second gas pipe 22 built in the second mixing chamber 2 so that the gas can be transported through the first gas pipe 12. To the second gas pipe 22.
  • a gas nozzle 4 is disposed on the first gas pipe 12 and the second gas pipe 22, and the gas is injected into the mixer by the gas nozzle 4 of the gas pipe disposed in the mixer, and the gas nozzle 4 faces and enters the mixing chamber 1.
  • the air flow in the intersection 2 intersects, so that the gas flow in the mixing chambers 1, 2 and the air flow are cross-mixed, and the gas flow changes direction after mixing and flows along with the air flow, thus increasing the gas in the mixing chambers 1, 2
  • the length of the actual mixing path with the air thereby achieving both a good mixing of the gas and the air and reducing the overall volume of the device.
  • the present invention can also be arranged with three, four or more mixing chambers side by side, as long as the gas flow in the mixing chambers 1, 2 can be cross-mixed with the air flow.
  • gas pipes 12, 22 are vertically disposed on the air circulation paths of the mixing chambers 1, 2, respectively, to further fully mix the gas and the air, and further reduce the overall volume of the burner.
  • the first gas pipe 12 is in communication with the second gas pipe 22, and the second gas pipe 22 is connected to the first gas pipe 12 to control the second gas pipe 22. Closed gas on/off valve 5.
  • the first gas pipe 12 is a normally open pipe, that is, the first gas pipe 12 is kept in a normally open state
  • the second gas pipe 22 is a control switch pipe, that is, the second gas pipe 22 can be controlled to open and close by the gas on/off valve 5, thereby realizing Segmented combustion function. In this way, not only the load regulation ratio of the system is improved, but also the probability of the condensed water generated by the flue gas is effectively reduced.
  • the gas pipeline can also be adapted to set three, four or more, each The gas pipelines are sequentially connected, and the connected gas pipeline includes at least one control switch pipeline and at least one normally open pipeline, the normally open pipeline is connected with the gas transmission pipeline of the peripheral, and the control control switch pipeline is arranged on the connection pipe of the control switch pipeline. Open and close gas on-off valve.
  • the gas on-off valve 5 is a solenoid valve, and the sealing member 501 of the solenoid valve is movable from the outside of the second gas pipe 22 to the first gas pipe. Between 12 and the second gas pipe 22, the function of closing the air inlet of the second gas pipe 22 is realized, and the closing function of the second gas pipe 22 is realized. When it is necessary to open the second gas pipe 22, it is only necessary to move the sealing member 501 to one side of the second gas pipe 22, so that the first gas pipe 12 and the second gas pipe 22 are in return communication.
  • the gas on-off valve 5 can also be a shut-off valve, a ball valve, a disc valve, a plunger valve or other known on-off valve, as long as the opening and closing function of the control switch pipe can be realized, the present invention does not limit this. .
  • the ratio of the sum of the area of the gas nozzles 4 on the first gas pipe 12 to the sum of the areas of the gas nozzles 4 on the second gas pipe 22 is between 1:3 and 1:1.
  • the first mixing chamber 1 and the second mixing chamber 2 are separated by a partition plate 6, and the first gas pipe 12 and the second gas pipe 22 are installed through the partition plate 6.
  • the holes are disposed through the first mixing chamber 1 and the second mixing chamber 2 to make the structure more compact.
  • a uniform wind structure is provided at an upper portion of the first mixing chamber 1 and the second mixing chamber 2, so that the mixed gas is uniformly delivered to the burner through the uniform wind structure.
  • the uniform wind structure is a flat plate having a porous structure.
  • the first mixing chamber 1 and the second mixing chamber 2 are of a venturi type, and the venturi-type mixing chambers 1, 2 have a tapered throat section 7 and a divergent mixing section 8 .
  • the gas spout 4 is located on the front side of the venturi throat section 7, where the gas and air are first mixed in this area, and then accelerated by the compression of the throat section 7, expanding at the throat section 7 downstream. And premix the gas and air at the large arc corners of the subsequent venturi-type mixing chamber and the deformation of several runners, and mix well before reaching the burner to ensure sufficient combustion and low pollutant emissions.
  • FIG. 5 it is a schematic structural view of a second embodiment of the multi-chamber gas-air mixing device of the present invention.
  • the mixing chamber can be further divided into a first mixing chamber 1, a second mixing chamber 2, a third mixing chamber 3, and further includes an air inlet, a first gas conduit 12, and a second The gas pipe 22, the third gas pipe 32, the first electromagnetic valve 51, the second electromagnetic valve 52, and the mixed gas outlet.
  • the first gas pipeline is respectively connected with the second gas pipeline 22 and the third gas pipeline 32
  • the gas sealing platform is arranged at the joint, and the joint and separation control of the sealing member 501 of the electromagnetic valves 51 and 52 and the gas sealing platform are second.
  • the gas pipe 22 and the third gas pipe 32 are opened and closed.
  • the mixing device can be divided into three sections, and the combustion load adjustment ratio is further improved, which is more beneficial to the high power system.
  • the multi-chamber gas-air mixing device of the present invention can be manufactured by integral molding, and the material can be aluminum or
  • Plastics such as PPS.
  • the invention integrates the gas injection device and the mixer, so that the gas-air mixer has a combustion segmentation function, which makes the efficiency under a large load high, not only improves the load regulation ratio of the system, but also causes a small load. No condensate is generated, which effectively reduces the probability of condensate from being generated by the flue gas.
  • the gas passage is built into the mixer to make the mixing of gas and air more uniform, effectively reducing the emission of combustion pollutants, and the mixer size is optimized. , to achieve the purpose of reducing the size of the system, so that the overall cost is greatly reduced, with significant technological progress.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
  • Regulation And Control Of Combustion (AREA)

Abstract

一种多腔燃气空气混合装置，包括至少两个混合腔（1，2），各个混合腔（1，2）分别具有空气入口（11，21）和与燃烧器相连通的混合气出口。各个混合腔（1，2）内分别设置有燃气管道（12，22），在各燃气管道（12，22）上均开设有燃气喷口（4），燃气喷口（4）的朝向与进入混合腔（1，2）内的空气流向相交叉。该装置将燃气空气混合器有效分段，实现了大的负荷调节比。

Description

一种多腔燃气空气混合装置
技术领域
本发明涉及一种应用于全预混燃烧的燃气热水器的多腔燃气空气混合装置，尤其是 一种能够实现分段燃烧功能的混合器， 属于热水器技术领域。 背景技术
全预混燃烧系统是指将燃气和空气一次性混合均匀后进行燃烧的系统。 其特点在 于： 具有较小的过量空气系数（即实际所需空气量与理论所需空气量的比值， 一般小于 1. 5 )， 较低的污染物（N0x， CO)排放， 燃烧强度大、火焰短， 燃烧的面积热负荷较大， 燃烧噪音小等多种优点。 在燃气热水器领域， 全预混燃烧系统的应用已有一定的历史， 并且随着各种性能要求的提高， 特别是国家对污染物排放的控制越来越严格， 其发展前 景较为乐观。
然而， 现有的全预混燃烧系统不能适用于非冷凝式产品。全预混燃烧器和常见的部 分预混燃烧器有很大不同， 其材料一般为陶瓷、 不锈钢板、碳纤维板和铁铬铝金属丝网 等。 其特征在于在较小的过量空气系数下， 可以燃烧的很充分； 同时， 由于供燃烧的空 气少， 导致火焰温度比部分预混燃烧的温度高 30CTC左右。 较高的烟气温度和较少的烟 气量（过量空气系数） 大大提高了换热效率， 容易产生冷凝水，因此全预混燃烧方式往 往用于冷凝式燃烧系统。
设定出现冷凝水的概率为 P， 则
P=f (Q, A, α ) ·
其中 Q为输入负荷， A为换热器有效换热面积， α 为过量空气系数。
对一个正常工作的热水器而言， Α的值是固定的， 因此上式可以简化为 P=f (Q， α ) 0 即冷凝水产生的概率由系统的过量空气系数与输入负荷确定： 1 )输入负荷在一定范围 内线性变化时， 负荷越小， 相对换热面积越大， 换热效率越高， 产生冷凝水的概率就越 高， 对一个确定的燃烧系统， 过量空气系数不变时， 若输入负荷小到某一值， 必然出现 冷凝水。 2 )过量空气系数与冷凝水的产生有直接关系。 一般来说， 露点温度 Td是衡量 是否会产生冷凝水的重要参数， 烟气温度小于露点温度时必然产生冷凝水， 烟气露点则 与烟气含湿量（ds )成正比， 烟气含湿量等于烟气中水蒸汽质量与总烟气质量之比， 显 然， 过量空气系数越大， 总烟气质量越大， 烟气含湿量越小， 烟气露点温度则越低， 产 生冷凝水的概率就越低。 因此， 对于非冷凝式产品， 避免产生冷凝水就要从这两个方面 入手。
对传统的部分预混式燃烧， 燃烧系统大都由若干独立的燃烧器构成， 通过控制部分 燃烧器的启停， 可以完成最大和最小负荷之间的调节， 如图 1所示， 为现有的部分预混 式分段燃烧的特征图， 图中横坐标 I为调节电流值， 纵坐标 Q为输入负荷， 将一个共有 15个燃烧器的系统分为段 1 (燃烧器数目 nl=5 )和段 2 (燃烧器数目 n2=15 )，可以大大 提高系统的调节比。且当最大负荷时， 所有的燃烧器工作，其过量空气系数一般约为 2; 最小负荷时， 只有部分燃烧器工作， 另外一部分燃烧器只通过空气， 此时过量空气系数 可达 10以上， 因此这种系统产生冷凝水的可能性非常小。
但对全预混燃烧而言， 在整个负荷范围内， 其过量空气系数均维持在 1. 5左右， 过 高则离焰， 过低则熄火或回火， 这会使小负荷时冷凝水出现的概率大大增加。根据实验 结果， 对一个定型的换热系统， 只有当过量空气系数超过 2时冷凝水出现的可能才会降 低。 因此， 如何将全预混燃烧系统应用于非冷凝式产品， 又没有产生冷凝水的风险， 是 本发明要解决的课题之一。
一篇中国专利申请号为 200310101740，发明名称为《能够多级控制的燃气燃烧器》， 公开了一种能够多级控制的燃气燃烧器， 该燃烧器由多个独立的管型燃烧器组成， 每个 单独的管型燃烧器内又设置混合气供给装置， 在混合气供给装置外又设置文氏管（文丘 里管）和歧管， 分别控制燃气和空气的供给与混合。 该发明虽然能够解决分段的问题， 但结构复杂、 体积庞大， 对制造和装配工艺要求较高， 成本也相应较高。
另一篇中国专利申请号为 201310135997，发明名称为《正压引射式全预混燃烧供热 装置》也公开了相似的结构。
综上所述， 开发一种可分段、负荷范围大、不易产生冷凝水、体积小巧、成本低廉、 且安全可靠的预混燃烧系统， 是一项有意义的工作， 设计优秀的燃气 /空气混合器则是 其中的一个关键步骤。 发明内容
本发明的目的是提供一种多腔燃气空气混合装置， 该混合装置能够减小体积， 并能 够将燃气和空气充分混合， 且在燃烧断面上均匀分布； 还具有燃烧分段功能， 使小负荷 时换热器上不产生冷凝水， 延长系统使用寿命。 为达到上述目的， 本发明提出一种多腔燃气空气混合装置， 包括至少两个混合腔， 各个所述混合腔分别具有空气入口、 与燃烧器相连通的混合气出口， 各个所述混合腔分 别内置设有燃气管道， 在各所述燃气管道上均开设有燃气喷口， 所述燃气喷口的朝向与 进入所述混合腔内的空气流向相交叉。
如上所述的多腔燃气空气混合装置，其中，至少两个所述混合腔内的燃气管道连通， 所述相连通的燃气管道包括至少一个控制开关管道。 如上所述的多腔燃气空气混合装 置， 其中， 所述相连通的燃气管道还包括至少一个常开管道， 所述常开管道与外设的燃 气输送管道相连接，在所述控制开关管道与所述常开管道之间设有控制所述控制开关管 道启闭的燃气通断阀。
如上所述的多腔燃气空气混合装置， 其中， 所述燃气通断阀是电磁阀， 所述电磁阀 的密封部件能移动的封堵于所述控制开关管道与所述常开管道之间。
如上所述的多腔燃气空气混合装置， 其中， 所述燃气管道垂直设置于所述混合腔的 空气流通路径上。
如上所述的多腔燃气空气混合装置， 其中， 所述混合腔呈文丘里型， 所述文丘里型 混合腔具有渐缩状的喉口段和渐扩状的混合段。
如上所述的多腔燃气空气混合装置， 其中， 所述至少两个混合腔并排设置， 相邻的 两个所述混合腔之间通过隔板相分隔，所述燃气管道通过所述隔板开设的安装孔贯穿设 置于所述混合腔内。
如上所述的多腔燃气空气混合装置， 其中， 在所述混合腔的上部设有均风结构。 如上所述的多腔燃气空气混合装置， 其中， 所述均风结构为具有多孔结构的平板。 如上所述的多腔燃气空气混合装置， 其中， 所述至少两个混合腔包括第一混合腔和 第二混合腔， 在所述第一混合腔内设有第一燃气管道， 所述第二混合腔内设有所述第二 燃气管道， 所述第二燃气管道与所述第一燃气管道连通， 所述第二燃气管道与所述第一 燃气管道上均有所述燃气喷口，且所述第二燃气管道与所述第一燃气管道之间设置所述 燃气通断阀。
如上所述的多腔燃气空气混合装置， 其中， 所述第一燃气管道上的燃气喷口面积之 和与所述第二燃气管道上的燃气喷口面积之和的比值为 1 : 3〜1 : 1之间。
与现有技术相比， 本发明具有以下特点和优点：
1、 本发明通过多个混合腔将燃气空气混合器有效分段， 实现大的负荷调节比， 在 各负荷段都不产生冷凝水， 提高了系统可靠性和寿命。 2、 本发明内置燃气通道既实现了控制开关管道燃料的主动控制， 又缩小了混合器 的体积， 大幅降低了成本。
3、本发明燃气喷口的朝向与进入混合腔内的空气流向相交叉，使燃气与空气充分混 合。
综上所述， 本发明和已有技术相比， 解决了常规全预混燃烧系统不能分段的问题， 采用燃气通道内置于混合器的结构，通过燃气通断阀有效控制上述控制开关管道燃料的 供给， 结构紧凑、 成本低廉、 安全性高， 具有突出的实质性特点和显著的进步。 附图说明
在此描述的附图仅用于解释目的， 而不意图以任何方式来限制本发明公开的范围。 另外， 图中的各部件的形状和比例尺寸等仅为示意性的， 用于帮助对本发明的理解， 并 不是具体限定本发明各部件的形状和比例尺寸。 本领域的技术人员在本发明的教导下， 可以根据具体情况选择各种可能的形状和比例尺寸来实施本发明。
图 1为现有的部分预混式分段燃烧的特征图；
图 2为本发明多腔燃气空气混合装置的实施例一的立体结构示意图；
图 3为图 2的 A-A断面结构示意图；
图 4为图 3的 B-B断面结构示意图；
图 5为本发明多腔燃气空气混合装置的实施例二的结构示意图。
附图标记说明：
1-第一混合腔； 11-第一空气入口； 12-第一燃气管道；
2-第二混合腔； 21-第二空气入口； 22-第二燃气管道；
3-第三混合腔； 32-第三燃气管道；
4-燃气喷口； 5-燃气通断阀； 501-密封部件； 51-第一电磁阀； 52-第二电磁阀； 6-隔板； 7-喉口段； 8-混合段。 具体实施方式
结合附图和本发明具体实施方式的描述，能够更加清楚地了解本发明的细节。但是， 在此描述的本发明的具体实施方式， 仅用于解释本发明的目的， 而不能以任何方式理解 成是对本发明的限制。在本发明的教导下， 技术人员可以构想基于本发明的任意可能的 变形， 这些都应被视为属于本发明的范围。 本发明提出了一种多腔燃气空气混合装置， 包括至少两个混合腔， 各个混合腔分别 具有空气入口、 与燃烧器相连通的混合气出口， 各个混合腔分别内置设有燃气管道， 减 小了混合装置的整体体积。 在各燃气管道上均开设有燃气喷口， 燃气喷口的朝向与进入 混合腔内的空气流向相交叉。 这样， 使得空气与燃气在混合腔内充分混合。
如图 2至图 4所示， 图 2为本发明多腔燃气空气混合装置的实施例一的立体结构示 意图； 图 3为图 2的 A-A断面结构示意图； 图 4为图 3的 B-B断面结构示意图。 本发明 多腔燃气空气混合装置包括： 第一混合腔 1、 第二混合腔 2、 第一空气入口 11、 第二空 气入口 21、 第一燃气管道 12、 第二燃气管道 22、 燃气通断阀 5、 混合气出口 （图中未 示出） 。 第一混合腔 1和第二混合腔 2分别具有空气入口 11、 21和混合气出口， 空气 入口 11、 21与大气相连， 通过风机提供空气， 使得外界空气进入混合腔 1、 2中并沿混 合腔的内腔形成的空气通道流动。 混合气出口则与燃烧器相连， 以向混合腔提供混合燃 气。 如图 2、 图 3所示， 第一混合腔 1内置有第一燃气管道 12，第一燃气管道 12的一端 与燃气输送管道及燃气调节阀相连，图 3 中的箭头方向为燃气输入方向， 通过燃气调节 阀控制引入第一燃气管道 12的燃气量，第一燃气管道 12的另一端与内置于第二混合腔 2内的第二燃气管道 22相连， 使得燃气能够通过第一燃气管道 12输送至第二燃气管道 22。 在第一燃气管道 12、 第二燃气管道 22上均开设有燃气喷口 4， 燃气由置于混合器 中的燃气管道的燃气喷口 4射入混合器， 燃气喷口 4的朝向与进入混合腔 1、 2内的空 气流向相交叉， 使得混合腔 1、 2 内的燃气流与空气流相交叉混合， 燃气流在混合后改 变方向并随空气流一起流动， 这样就增加了混合腔 1、 2中燃气与空气的实际混合路径 的长度， 从而既实现了燃气与空气的充分混合， 又减少了装置的整体体积。 当然， 本发 明也可以设置并排三个、 四个或更多个混合腔， 只要能够保证混合腔 1、 2 内的燃气流 与空气流相交叉混合即可。
进一步的， 燃气管道 12、 22分别垂直设置于混合腔 1、 2的空气流通路径上， 进一 步使得燃气与空气的混合更加充分， 并进一步减少了燃烧器的整体体积。
在本实施例中， 如图 2、 图 3所示， 第一燃气管道 12与第二燃气管道 22连通， 第 二燃气管道 22与第一燃气管道 12之间设有控制第二燃气管道 22启闭的燃气通断阀 5。 第一燃气管道 12为常开管道， 即第一燃气管道 12保持常开状态， 第二燃气管道 22为 控制开关管道， 即第二燃气管道 22可通过燃气通断阀 5控制启闭， 实现了分段燃烧功 能。 这样， 不仅提高了系统的负荷调节比， 同时有效降低烟气产生冷凝水的概率。 在本 发明中， 根据混合腔数量的不同， 燃气管道也可以适应设置三个、 四个或更多个， 各个 燃气管道依次连通， 相连通的燃气管道包括至少一个控制开关管道和至少一个常开管 道， 常开管道与外设的燃气输送管道相连接， 在控制开关管道的连接管上设有控制控制 开关管道启闭的燃气通断阀。
进一步的， 如图 2、 图 3所示， 在本实施例中， 燃气通断阀 5是电磁阀， 电磁阀的 密封部件 501由第二燃气管道 22的外侧能移动的设置于第一燃气管道 12与第二燃气管 道 22之间， 起到封堵第二燃气管道 22进气口的作用， 实现第二燃气管道 22的闭合功 能。 当需要开启第二燃气管道 22时， 只需将密封部件 501移动至第二燃气管道 22的一 侧即可， 使得第一燃气管道 12与第二燃气管道 22恢复连通。 在本发明中， 燃气通断阀 5还可以采用截止阀、 球阀、 碟阀、 柱塞阀或其它公知的开关阀， 只要能够实现控制开 关管道的启闭功能即可， 本发明对此不作限制。
进一步的，第一燃气管道 12上的燃气喷口 4面积之和与第二燃气管道 22上的燃气 喷口 4面积之和的比值为 1： 3〜 1： 1之间。
进一步的， 如图 2、 图 3所示， 第一混合腔 1与第二混合腔 2之间通过隔板 6相分 隔，第一燃气管道 12与第二燃气管道 22通过隔板 6开设的安装孔贯穿设置于第一混合 腔 1与第二混合腔 2内， 使得结构更加紧凑。
进一步的， 在第一混合腔 1与第二混合腔 2的上部设有均风结构， 使得混合气通过 均风结构均匀地输送至燃烧器。 优选的， 均风结构为具有多孔结构的平板。
进一步的， 如图 4所示， 第一混合腔 1和第二混合腔 2呈文丘里型， 文丘里型混合 腔 1、 2具有渐缩状的喉口段 7和渐扩状的混合段 8。在本实施例中， 燃气喷口 4位于文 丘里喉口段 7前侧， 燃气与空气在该区域发生第一次混合， 随后经过喉口段 7的压缩加 速， 在喉口段 7下游处扩撒， 并在随后的文丘里型混合腔的大弧度拐角和若干流道变形 处对燃气和空气进行预混，在到达燃烧器之前充分混合，确保燃烧充分，污染物排放低。
在本发明另一个可选的实施例中， 如图 5所示， 为本发明多腔燃气空气混合装置的 实施例二的结构示意图。 本实施例与实施例一的不同之处在于， 混合腔可以进一步分为 第一混合腔 1、 第二混合腔 2、 第三混合腔 3， 还包括空气入口、 第一燃气管道 12、 第 二燃气管道 22、第三燃气管道 32、第一电磁阀 51、第二电磁阀 52、混合气出口。其中， 第一燃气管道分别与第二燃气管道 22、 第三燃气管道 32相连接， 连接处设置燃气密封 平台， 通过电磁阀 51、 52的密封部件 501与燃气密封平台的接合与分离控制第二燃气 管道 22、 第三燃气管道 32的启闭。 通过本实施例的上述结构设计， 可以将混合装置分 为三段， 进一步提高了燃烧负荷调节比， 对大功率系统更有益。 本发明的多腔燃气空气混合装置可以通过整体成型的方式制造， 材料可以是铝或
PPS等塑料。
综上所述， 本发明将燃气喷入装置和混合器一体化， 使燃气空气混合器具备燃烧分 段功能， 使大负荷下效率较高， 不仅提高了系统的负荷调节比， 同时因小负荷下不产生 冷凝水， 有效降低烟气产生冷凝水的概率； 同时， 燃气通道内置于混合器， 使燃气和空 气的混合更充分均匀， 有效降低了燃烧污染物的排放， 且混合器尺寸得到优化， 实现了 减小系统体积的目的， 使整体成本大幅降低， 具有显著的技术进步。
针对上述各实施方式的详细解释， 其目的仅在于对本发明进行解释， 以便于能够更 好地理解本发明， 但是， 这些描述不能以任何理由解释成是对本发明的限制， 特别是， 在不同的实施方式中描述的各个特征也可以相互任意组合， 从而组成其他实施方式， 除 了有明确相反的描述， 这些特征应被理解为能够应用于任何一个实施方式中， 而并不仅 局限于所描述的实施方式。

Claims

权利要求书
1、 一种多腔燃气空气混合装置， 包括至少两个混合腔， 各个所述混合腔分别具有 空气入口、 与燃烧器相连通的混合气出口， 其特征在于， 各个所述混合腔分别内置设有 燃气管道， 在各所述燃气管道上均开设有燃气喷口， 所述燃气喷口的朝向与进入所述混 合腔内的空气流向相交叉。
2、 如权利要求 1所述的多腔燃气空气混合装置， 其特征在于， 至少两个所述混合 腔内的燃气管道连通， 所述相连通的燃气管道包括至少一个控制开关管道。
3、 如权利要求 2所述的多腔燃气空气混合装置， 其特征在于， 所述相连通的燃气 管道还包括至少一个常开管道， 所述常开管道与外设的燃气输送管道相连接， 在所述控 制开关管道与所述常开管道之间设有控制所述控制开关管道启闭的燃气通断阀。
4、 如权利要求 3所述的多腔燃气空气混合装置， 其特征在于， 所述燃气通断阀是 电磁阀， 所述电磁阀的密封部件能移动的封堵于所述控制开关管道与所述常开管道之 间。
5、 如权利要求 1所述的多腔燃气空气混合装置， 其特征在于， 所述燃气管道垂直 设置于所述混合腔的空气流通路径上。
6、 如权利要求 1所述的多腔燃气空气混合装置， 其特征在于， 所述混合腔呈文丘 里型， 所述文丘里型混合腔具有渐缩状的喉口段和渐扩状的混合段。
7、 如权利要求 1所述的多腔燃气空气混合装置， 其特征在于， 所述至少两个混合 腔并排设置， 相邻的两个所述混合腔之间通过隔板相分隔， 所述燃气管道通过所述隔板 开设的安装孔贯穿设置于所述混合腔内。
8、 如权利要求 1所述的多腔燃气空气混合装置， 其特征在于， 在所述混合腔的上 部设有均风结构。
9、 如权利要求 8所述的多腔燃气空气混合装置， 其特征在于， 所述均风结构为具 有多孔结构的平板。
10、 如权利要求 1至 9中任一项所述的多腔燃气空气混合装置， 其特征在于， 所述 至少两个混合腔包括第一混合腔和第二混合腔， 在所述第一混合腔内设有第一燃气管 道， 所述第二混合腔内设有所述第二燃气管道， 所述第二燃气管道与所述第一燃气管道 连通， 所述第二燃气管道与所述第一燃气管道上均有所述燃气喷口， 且所述第二燃气管 道与所述第一燃气管道之间设置所述燃气通断阀。
11、 如权利要求 10所述的多腔燃气空气混合装置， 其特征在于， 所述第一燃气管 道上的燃气喷口面积之和与所述第二燃气管道上的燃气喷口面积之和的比值为 1： 3〜 1 : 1之间。
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109442406A (zh) * 2018-11-30 2019-03-08 唐山金沙燃烧热能股份有限公司 多头内混式超低氮燃烧装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110242957A (zh) * 2019-06-28 2019-09-17 广东万和热能科技有限公司 一种筒状全预混分段燃烧器及壁挂炉
CN114688744B (zh) * 2022-03-31 2024-04-12 广东万和新电气股份有限公司 燃气热水器及其分段切换性能测试方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0618013A (ja) * 1992-07-04 1994-01-25 Gastar Corp 予混合装置
JPH0875127A (ja) * 1994-09-07 1996-03-19 Matsushita Electric Ind Co Ltd 燃焼装置
JPH1089627A (ja) * 1996-09-12 1998-04-10 Tokyo Gas Co Ltd 元混合型ガス燃焼装置
JPH10227413A (ja) * 1997-02-17 1998-08-25 Rinnai Corp 燃焼装置
CN2722046Y (zh) * 2004-08-16 2005-08-31 上海城市燃气技术研究所 全预混式双通道二段火超强燃烧器

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6000933A (en) * 1997-04-04 1999-12-14 Frederick, Sr.; Charles B Variable burner orifice furnace manifold
KR100495505B1 (ko) 2002-10-22 2005-06-14 주식회사 경동보일러 다단제어를 구현하는 가스연소 버너
GB2398375A (en) * 2003-02-14 2004-08-18 Alstom A mixer for two fluids having a venturi shape
ITBO20100441A1 (it) * 2010-07-12 2012-01-13 Gas Point S R L Bruciatore a gas a pre-miscelazione
KR101214745B1 (ko) * 2011-03-25 2012-12-21 주식회사 경동나비엔 유로 분리형 가스-공기 혼합장치
KR101259764B1 (ko) * 2012-02-15 2013-05-07 주식회사 경동나비엔 연소기기용 듀얼 벤츄리
KR101320113B1 (ko) * 2012-02-28 2013-10-18 주식회사 경동나비엔 온수기용 듀얼 벤추리
KR101338179B1 (ko) * 2012-04-23 2013-12-09 주식회사 경동나비엔 턴다운비를 향상시킨 연소장치
CN103196218B (zh) 2013-04-18 2016-06-29 天津城市建设学院 正压引射式全预混燃烧供热装置
CN203628660U (zh) 2014-01-09 2014-06-04 艾欧史密斯(中国)热水器有限公司 一种多腔燃气空气混合装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0618013A (ja) * 1992-07-04 1994-01-25 Gastar Corp 予混合装置
JPH0875127A (ja) * 1994-09-07 1996-03-19 Matsushita Electric Ind Co Ltd 燃焼装置
JPH1089627A (ja) * 1996-09-12 1998-04-10 Tokyo Gas Co Ltd 元混合型ガス燃焼装置
JPH10227413A (ja) * 1997-02-17 1998-08-25 Rinnai Corp 燃焼装置
CN2722046Y (zh) * 2004-08-16 2005-08-31 上海城市燃气技术研究所 全预混式双通道二段火超强燃烧器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109442406A (zh) * 2018-11-30 2019-03-08 唐山金沙燃烧热能股份有限公司 多头内混式超低氮燃烧装置
CN109442406B (zh) * 2018-11-30 2023-09-22 唐山金沙燃烧热能股份有限公司 多头内混式超低氮燃烧装置

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