CN110529872B - Power station boiler waste heat utilization system based on inlet flue gas temperature communication control - Google Patents

Power station boiler waste heat utilization system based on inlet flue gas temperature communication control Download PDF

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CN110529872B
CN110529872B CN201810819057.2A CN201810819057A CN110529872B CN 110529872 B CN110529872 B CN 110529872B CN 201810819057 A CN201810819057 A CN 201810819057A CN 110529872 B CN110529872 B CN 110529872B
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heat
air preheater
flue gas
valve
air
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CN110529872A (en
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王逸隆
马军
江程
李言伟
连根款
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Suzhou Hailu Heavy Industry Co Ltd
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Suzhou Hailu Heavy Industry Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L15/00—Heating of air supplied for combustion
    • F23L15/04—Arrangements of recuperators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N3/00—Regulating air supply or draught
    • F23N3/002—Regulating air supply or draught using electronic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N3/00—Regulating air supply or draught
    • F23N3/06—Regulating air supply or draught by conjoint operation of two or more valves or dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
    • F28D15/046—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure characterised by the material or the construction of the capillary structure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F28D21/001—Recuperative heat exchangers the heat being recuperated from exhaust gases for thermal power plants or industrial processes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L2900/00—Special arrangements for supplying or treating air or oxidant for combustion; Injecting inert gas, water or steam into the combustion chamber
    • F23L2900/15043—Preheating combustion air by heat recovery means located in the chimney, e.g. for home heating devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2900/00—Special features of, or arrangements for controlling combustion
    • F23N2900/05005—Mounting arrangements for sensing, detecting or measuring devices
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air Supply (AREA)

Abstract

The invention provides a power station boiler waste heat utilization system capable of intelligently controlling and utilizing waste heat, which comprises an air preheater, a heat reservoir and a central controller, wherein the central controller is in data connection with a valve of the air preheater and a valve of the heat reservoir, a third temperature sensor is arranged at the position of a flue gas inlet of the air preheater, and the central controller automatically controls the opening degrees of the valve of the air preheater and the valve of the heat reservoir according to the temperature detected by the third temperature sensor. Through the operation, when the temperature of the flue gas is high, after the requirement of the preheated air is met, the redundant heat can be stored through the heat storage device, when the temperature of the flue gas is low, more flue gas can enter the air preheater to preheat the air, the requirement of the preheated air is ensured, and meanwhile, energy is saved.

Description

Power station boiler waste heat utilization system based on inlet flue gas temperature communication control
Technical Field
The invention discloses a part of project which is developed together with enterprises, is an improvement on the prior application, relates to the field of heat pipe waste heat recovery, and particularly relates to a control method and device for recovering flue gas waste heat by using a heat pipe.
Background
Along with the rapid development of economy in China, the energy consumption is increased day by day, the problem that the urban atmosphere quality is worsened day by day is more prominent, and the problems of saving energy and reducing the emission of harmful substances in the environment are urgent. In the common steam generation process, one of the main reasons of high energy consumption and serious pollution is that the exhaust gas temperature of the boiler flue gas is too high, and a large amount of energy is wasted, so that the waste heat of the boiler tail gas is recycled, the purposes of energy conservation and emission reduction are realized, and the environment can be protected. However, in the prior art, low-temperature corrosion may occur while the residual heat of the flue gas is satisfied, so how to avoid the low-temperature corrosion is an important problem, and meanwhile, if only to avoid the low-temperature corrosion, the residual heat in the flue gas is wasted too much in some cases, so that a problem of poor residual heat utilization effect occurs, and therefore, the above-mentioned related problems need to be solved urgently.
The heat pipe technology is a heat transfer element called a heat pipe invented by George Grover (George Grover) of national laboratory of Los Alamos (Los Alamos) in 1963, fully utilizes the heat conduction principle and the rapid heat transfer property of a phase change medium, quickly transfers the heat of a heating object to the outside of a heat source through the heat pipe, and the heat conduction capability of the heat transfer element exceeds the heat conduction capability of any known metal. Compared with the most commonly used shell-and-tube heat exchanger in the coal-fired flue gas waste heat recovery, the heat pipe heat exchanger has the advantages of high heat transfer efficiency, compact structure, small pressure loss, being beneficial to controlling dew point corrosion and the like, and has more potential in the coal-fired flue gas waste heat recovery.
The heat exchange fluid of the heat pipe in heat exchange is a steam-water mixture. The heat pipe is in the evaporation process, and inevitable can carry liquid to the steam end in, simultaneously because the condensation that releases heat of condensation end to there is liquid in making the condensation end, liquid inevitable mixes with steam, thereby makes the fluid in the heat pipe be vapour-liquid mixture, and vapour-liquid mixture exists and leads to the vapour to mix into a group, and the heat transfer ability descends between with the liquid, great influence the efficiency of heat transfer.
In the boiler waste heat utilization system in the prior art, a lack of research on intelligent control is particularly concerned with intelligent control, such as heat distribution, in the case where a plurality of waste heat utilization devices exist simultaneously.
Aiming at the problems, the invention is improved on the basis of the prior invention, and provides a boiler waste heat utilization device with a novel intelligent control structure, which makes full use of a heat source, reduces energy consumption and realizes intelligent control.
Disclosure of Invention
In order to solve the problems, the invention is improved on the basis of the invention, and provides a boiler waste heat utilization device with a new structure so as to realize full utilization and intelligent control of waste heat.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a power station boiler waste heat utilization system comprises an air preheater and a heat reservoir, wherein the air preheater is arranged on a main pipeline of a flue, the heat reservoir is arranged on an auxiliary pipeline, the main pipeline and the auxiliary pipeline form a parallel pipeline, flue gas in the flue respectively enters the air preheater and the heat reservoir of the main pipeline and the auxiliary pipeline, steam is generated in the air preheater, heat is stored in the heat reservoir, and the flue gas after heat exchange in the air preheater and the heat reservoir converges and enters the flue;
the system comprises an air preheater valve, a heat reservoir valve, a central controller and a third temperature sensor, wherein the air preheater valve is arranged at the position of an inlet of an air preheater of a main flue and used for controlling the flow of flue gas entering the air preheater, the heat reservoir valve is arranged at the position of an inlet pipe of a heat reservoir of an auxiliary pipeline and used for controlling the flow of the flue gas entering the heat reservoir, the central controller is in data connection with the air preheater valve and the heat reservoir valve, and the third temperature sensor is arranged at the position of the flue gas inlet of the air preheater and used for measuring the temperature of the flue gas entering the air preheater; the third temperature sensor is in data connection with the central controller, and the central controller automatically controls the valve opening degrees of the air preheater valve and the heat reservoir valve according to the temperature detected by the third temperature sensor.
Preferably, when the temperature measured by the third temperature sensor is lower than a certain temperature, the central controller controls the valve of the air preheater to increase the opening degree, and controls the valve of the heat reservoir to decrease the opening degree so as to increase the flow of the flue gas entering the air preheater; when the temperature measured by the third temperature sensor is higher than a certain temperature, the central controller controls the valve of the air preheater to reduce the opening degree, and controls the valve of the heat reservoir to increase the opening degree simultaneously so as to reduce the flow of the flue gas entering the air preheater.
Preferably, the central controller controls the blower to stop operating if the temperature detected by the first temperature sensor is lower than the temperature detected by the second temperature sensor. If the temperature detected by the first temperature sensor is higher than the temperature detected by the second temperature sensor, the central controller controls the fan to start running.
Preferably, when the central controller detects that smoke passes through the pipeline, the central controller automatically controls the fan to stop running; when the central controller detects that no smoke passes through the pipeline, the central controller controls the upstream valve and the downstream valve to be closed, the pipeline where the air preheater and the heat reservoir are located forms a circulating pipeline, and the central controller automatically controls the fan to start to operate.
Preferably, the air preheater comprises a heat pipe, a flue gas channel and an air channel, the heat pipe comprises an evaporation end and a condensation end, the condensation end is arranged in the air channel, and the evaporation end is arranged in the flue; the evaporation end absorbs the waste heat of the flue gas in the boiler flue, the heat is transferred to the air in the air channel through the condensation end, and the preheated air enters the boiler hearth for supporting combustion.
Preferably, a stabilizing device is arranged in the heat collecting tube, the stabilizing device is of a sheet structure, and the sheet structure is arranged on the cross section of the heat collecting tube; the stabilizing device is composed of a square through hole and a regular octagonal through hole, the side length of the square through hole is equal to that of the regular octagonal through hole, four sides of the square through hole are respectively sides of four different regular octagonal through holes, and four mutually spaced sides of the regular octagonal through hole are respectively sides of four different square through holes.
Preferably, the cross section of the heat collecting pipe is square.
Preferably, the distance between adjacent stabilizers is K1, the side length of the square is B1, the heat pipe has a square cross section, the side length of the heat pipe is B2, the heat pipe forms an acute angle a with the horizontal plane, and the distance between the centers of the adjacent heat pipes is K2, which satisfies the following requirements:
c*K2/B2＝d*(K1/B2)2+e-f*(K1/B2)3-h*(K1/B2)；
wherein d, e, f, h are parameters,
1.239<d<1.240,1.544<e<1.545,0.37<f<0.38,0.991<h<0.992；c＝1/cos(A)nwherein 0.090<n<0.098, preferably n ═ 0.093.
11<B2<46mm；
1.9<B1<3.2mm；
18<K1<27mm。
16<K2<76mm。
Compared with the prior art, the invention has the following advantages:
1) through the operation, when the temperature of the flue gas is high, after the requirement of the preheated air is met, the redundant heat can be stored through the heat storage device, when the temperature of the flue gas is low, more flue gas can enter the air preheater to preheat the air, the requirement of the preheated air is ensured, and meanwhile, energy is saved.
2) The invention provides a power station boiler waste heat utilization system of a novel structure stabilizing device combining a novel square through hole and a novel regular octagon through hole, wherein the included angles formed by the edges of the formed square hole and the regular octagon hole are more than or equal to 90 degrees through the square and the regular octagon, so that fluid can fully flow through each position of each hole, and the short circuit of fluid flowing is avoided or reduced. The invention separates the two-phase fluid into liquid phase and gas phase by the stabilizing device with a novel structure, divides the liquid phase into small liquid groups, divides the gas phase into small bubbles, inhibits the backflow of the liquid phase, promotes the smooth flow of the gas phase, plays a role in stabilizing the flow and improves the heat exchange effect. Compared with the stabilizing device in the prior art, the stabilizing device further improves the flow stabilizing effect, strengthens heat transfer and is simple to manufacture.
3) According to the invention, through reasonable layout, the square and regular octagonal through holes are uniformly distributed, so that the fluid on the whole cross street is uniformly divided, and the problem of nonuniform division of the annular structure along the circumferential direction in the prior art is avoided.
4) The invention ensures that the large holes and the small holes are uniformly distributed on the whole cross section by uniformly distributing the square holes and the regular octagonal holes at intervals, and ensures that the separation effect is better by changing the positions of the large holes and the small holes of the adjacent stabilizing devices.
5) According to the invention, the stabilizing device is of a sheet structure, so that the stabilizing device is simple in structure and low in cost.
6) According to the invention, the optimal relation size of the parameters is researched by setting the regular changes of the parameters such as the distance between adjacent stabilizing devices, the side length of the hole of the stabilizing device, the pipe diameter of the heat absorbing pipe, the pipe spacing and the like in the height direction of the heat absorbing pipe, so that the current stabilizing effect is further achieved, the noise is reduced, and the heat exchange effect is improved.
7) The invention realizes the optimal relational expression of the heat exchange effect under the condition of meeting the flow resistance by widely researching the heat exchange rule caused by the change of each parameter of the stabilizing device.
8) The waste heat utilization device with the novel structure is provided, and the uniform pressure, the uniform distribution of the fluid flow and the uniform distribution of the fluid motion resistance in each heat pipe are ensured by arranging the flow equalizing pipe between the heat pipes.
Drawings
FIG. 1 is a schematic diagram of an air preheater according to the present invention.
Fig. 2 is a schematic diagram of the intelligent control of the flue gas waste heat utilization device.
FIG. 3 is a schematic cross-sectional view of a stabilization device according to the present invention;
FIG. 4 is a schematic view of another cross-sectional configuration of the stabilization device of the present invention;
FIG. 5 is a schematic view of the arrangement of the stabilizing device of the present invention within a heat pipe;
FIG. 6 is a schematic cross-sectional view of the arrangement of the stabilization device of the present invention within a heat pipe;
fig. 7 is a schematic cross-sectional view of a heat pipe with a flow equalizer tube according to the present invention.
FIG. 8 is a schematic structural view of the flue gas waste heat utilization device with a bypass flue according to the present invention.
In the figure: 1 air preheater, 2 heat reservoirs, 3 central controller, 4 stabilizing devices, 5 air preheater valves, 6 upstream valves, 7 downstream valves, 8 air outlets, 9 air inlets, 10 heat pipes, 11 shells, 12 main pipelines, 13 auxiliary pipelines, 14 flues, 15 bypass valves, 16 air channels, 17 heat reservoir valves and 18 flow equalizing pipes
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings.
In this document, "/" denotes division and "×", "denotes multiplication, referring to formulas, if not specifically stated.
The following detailed description of embodiments of the invention refers to the accompanying drawings.
The utility model provides a power plant boiler flue gas waste heat utilization system, waste heat utilization system includes air heater 1, air heater 1 includes heat pipe 10, flue gas passageway 14 and air channel 16, heat pipe 10 includes evaporating end 101 and condensing end 102, condensing end 102 sets up in air channel 12, and evaporating end 101 sets up in the flue. The evaporation end 101 absorbs the residual heat of the flue gas in the boiler flue, and transfers the heat to the air in the air channel 12 through the condensation end 102. And the preheated air enters a boiler hearth to support combustion.
When the heat pipe is in operation, the heat pipe absorbs heat from flue gas through the evaporation end 101, then releases the heat to air at the condensation end, condenses fluid, and enters the evaporation end 101 under the action of gravity.
In the operation process of the waste heat utilization device, fluid distribution is uneven, in the heat collection process, different heat pipes absorb different heat, so that the temperatures of fluids in different heat pipes are different, and in some heat pipes, even the fluids, such as water, are in a gas-liquid two-phase state, and the fluids in some heat pipes are still liquid, so that the pressure in the heat pipes is increased because the fluids are changed into steam, and therefore, the fluids can flow in the heat pipes mutually by arranging the flow equalizing pipes among the heat pipes, so that the pressure distribution in all the heat pipes is balanced, and the fluid distribution can be promoted to be balanced.
Alternatively, as shown in fig. 8, a uniform flow tube 18 is disposed between the heat pipes. A flow equalizing pipe 18 is disposed between at least two adjacent heat pipes 10. In the research, it is found that in the process of heat absorption and heat release of the evaporation tube, the heat absorption amount and the heat release amount of the heat absorption and heat release tubes at different positions are different, so that the pressure or the temperature between the heat tubes 10 is different, which may cause the temperature of some heat tubes 10 to be too high, resulting in a shortened service life, and once the heat tubes 10 have a problem, the problem that the whole waste heat utilization system cannot be used may occur. According to the invention, through a great deal of research, the flow equalizing pipes 18 are arranged on the adjacent heat pipes, so that under the condition that the pressures of the heat pipes are different due to different heating, the fluid in the heat pipe 10 with high pressure can quickly flow to the heat pipe 10 with low pressure, thereby keeping the overall pressure balance and avoiding local overheating or overcooling.
Preferably, a plurality of uniform flow pipes 18 are disposed between adjacent heat pipes 10 from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10. Through setting up a plurality of flow equalizing pipes, can make the continuous balanced pressure of fluid in the heat absorption evaporation process, guarantee the pressure balance in the whole heat pipe.
Preferably, the distance between adjacent uniform flow tubes 18 decreases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10 at the evaporation end 101. The purpose is to arrange more flow equalizing pipes, because the fluid continuously absorbs heat along with the upward flow of the fluid, and the pressure in different heat pipes is more and more uneven along with the continuous heat absorption of the fluid, so that the pressure equalization can be ensured to be achieved as soon as possible in the flowing process of the fluid through the arrangement.
Preferably, at the evaporation end 101, the distance between adjacent uniform flow tubes decreases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10 to a greater extent. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, the diameter of the equalizer 18 increases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10 at the evaporation end 101. The purpose is to ensure a larger communication area, because the fluid continuously absorbs heat to generate steam along with the upward flow of the fluid, and the temperature and pressure in different heat pipes are more and more uneven along with the continuous difference of the steam, so that the pressure balance can be ensured to be achieved as soon as possible in the flowing process of the fluid through the arrangement.
Preferably, the diameter of the equalizer 18 increases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10 to a greater extent at the evaporation end 101. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, at the condensation end 102, the distance between adjacent equalization tubes 18 increases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10. The purpose is to arrange fewer flow equalizing pipes and reduce the cost. Because the steam in the heat pipe continuously releases heat and condenses along with the upward lower part of the condensation end 102, and the pressure in the heat pipe is smaller and smaller along with the continuous heat release of the fluid, the phenomenon of non-uniformity is more and more alleviated, materials can be saved through the arrangement, the flow equalizing pipe is arranged according to the pressure change, and the pressure equalization can be achieved as soon as possible in the flowing process of the fluid.
Preferably, at the condensation end 102, the distance between adjacent uniform flow tubes increases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, the diameter of the equalizer 18 decreases from the evaporator end of the heat pipe 10 to the condenser end of the heat pipe 10 at the condenser end 102. The purpose is to ensure reduced communication area and reduce cost. The same principle as the distance from the front is increasing.
Preferably, the diameter of the equalizer 18 decreases from the evaporator end of the heat pipe 10 to the condenser end of the heat pipe 10 by a larger and larger amount at the condenser end 102. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Because the heat transfer of steam in the heat pipe for vapour-liquid two-phase flow appears in the heat pipe, on the one hand, the heat pipe is in the evaporation process, inevitable can carry liquid to the heat pipe in, simultaneously because the exothermic condensation of condensation end, thereby make to have liquid in the condensation end, liquid is inevitable in getting into steam, thereby make the fluid in the heat pipe be vapour-liquid mixture, the heat pipe can be because of the incondensable gas that ageing produced at the operation in-process simultaneously, the incondensable gas generally rises to the condensation end on heat pipe upper portion, the existence of incondensable gas leads to the pressure increase in the heat pipe condensation end, pressure makes liquid flow in the heat pipe. Greatly influencing the heat exchange efficiency. Therefore, the present invention adopts a new structure to separate vapor phase and liquid phase, so that the heat exchange is enhanced.
A stabilizing device 4 is arranged in the heat pipe, and the structure of the stabilizing device 4 is shown in figures 2 and 3. The stabilizing device 4 is a sheet-like structure which is arranged over the cross section of the heat pipe 10; the stabilizing device 4 is composed of a square and regular octagonal structure, so that a square through hole 41 and a regular octagonal through hole 42 are formed. The side length of the square through hole 41 is equal to the side length of the regular octagonal through hole 42 as shown in fig. 2, the four sides 43 of the square through hole are the sides 43 of four different regular octagonal through holes, respectively, and the four mutually spaced sides 43 of the regular eight deformed through hole are the sides 43 of four different square through holes, respectively.
The invention adopts a stabilizing device with a novel structure, and has the following advantages:
1) the invention provides a novel structure stabilizing device combining a square through hole and a regular octagon through hole, wherein the included angles formed by the edges of the formed square hole and the regular octagon hole are larger than or equal to 90 degrees through the square and the regular octagon, so that fluid can fully flow through each position of each hole, and the short circuit of the fluid flow is avoided or reduced. The two-phase fluid is separated into the liquid phase and the gas phase by the stabilizing device with the novel structure, the liquid phase is separated into small liquid masses, the gas phase is separated into small bubbles, the backflow of the liquid phase is inhibited, the gas phase is enabled to flow smoothly, the flow stabilizing effect is achieved, the vibration and noise reducing effect is achieved, and the heat exchange effect is improved. Compared with the stabilizing device in the prior art, the stabilizing device further improves the flow stabilizing effect, strengthens heat transfer and is simple to manufacture.
2) According to the invention, through reasonable layout, the square and regular octagonal through holes are uniformly distributed, so that the fluid on the whole cross street is uniformly divided, and the problem of nonuniform division of the annular structure along the circumferential direction in the prior art is avoided.
3) According to the invention, the square holes and the regular octagonal through holes are uniformly distributed at intervals, so that the large holes and the small holes are uniformly distributed on the whole cross section, and the separation effect is better through the position change of the large holes and the small holes of the adjacent stabilizing devices.
4) According to the invention, the stabilizing device is of a sheet structure, so that the stabilizing device is simple in structure and low in cost.
By arranging the annular stabilizing device, the invention equivalently increases the internal heat exchange area in the heat pipe, strengthens the heat exchange and improves the heat exchange effect.
The invention divides the gas phase and the liquid phase at all cross section positions of all heat exchange tubes, thereby realizing the contact area between the division of a gas-liquid interface and a gas phase boundary layer and a cooling wall surface on the whole heat exchange tube section and enhancing the disturbance, greatly reducing the noise and the vibration and strengthening the heat transfer.
Preferably, the stabilizing means comprises two types, as shown in figures 3 and 4, the first type being a square central stabilizing means, the square being located in the centre of the heat pipe or condenser tube, as shown in figure 4. The second is a regular octagonal central stabilizer, the regular octagon being located at the center of the heat pipe or condenser tube, as shown in fig. 3. As a preference, the two types of stabilizing means are arranged next to one another, i.e. the types of stabilizing means arranged next to one another differ. I.e. adjacent to the square central stabilizer is a regular octagonal central stabilizer, and adjacent to the regular octagonal central stabilizer is a square central stabilizer. According to the invention, the square holes and the regular octagon holes are uniformly distributed at intervals, so that the large holes and the small holes are uniformly distributed on the whole cross section, and through the position change of the large holes and the small holes of the adjacent stabilizing devices, the fluid passing through the large holes next passes through the small holes, and the fluid passing through the small holes next passes through the large holes to be further separated, so that the mixing of vapor and liquid is promoted, and the separating and heat exchanging effects are better.
Preferably, the heat pipe 10 is square in cross-section.
Preferably, a plurality of stabilizers are disposed in the evaporation end, and the distance between the stabilizers is gradually reduced from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10 at the evaporation end 101. Setting the distance from the evaporation end of the heat pipe to be H, and the distance between adjacent stabilizing devices to be S, S is F1(H) I.e. S is a function of the height H as a variable, S' is the first derivative of S, satisfying the following requirements:
S’<0；
the main reason is that the liquid in the heat pipe is heated continuously to generate steam, and in the rising process, the steam is increased continuously, so that the steam in the gas-liquid two-phase flow is increased, because the steam phase in the gas-liquid two-phase flow is increased, the heat exchange capacity in the heat pipe is weakened relatively along with the increase of the steam phase, and the vibration and the noise thereof are increased continuously along with the increase of the steam phase. The distance between adjacent stabilizers to be provided is therefore shorter and shorter.
Through the experiment discovery, through foretell setting, both can reduce vibrations and noise to the at utmost, can improve the heat transfer effect simultaneously.
It is further preferred that the distance between adjacent stabilizers increases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10 at the evaporation end 101. I.e. S "is the second derivative of S, the following requirements are met:
S”>0；
through the experiment, the vibration and the noise of about 7% can be further reduced, and the heat exchange effect of about 8% is improved.
Preferably, a plurality of stabilizers are disposed in the evaporation end 101, and the side length of the square in the evaporation end 101 decreases from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10. The distance from the lower end of the heat pipe is H, the side length of the square is C, and C is F2(H) And C' is the first derivative of C, and meets the following requirements:
C’<0；
further preferably, at the evaporation end 101, the side length of the square is gradually increased from the evaporation end of the heat pipe 10 to the condensation end of the heat pipe 10. C' is the second derivative of C, and meets the following requirements:
C”>0。
see the previous variation in the pitch of the stabilizer for specific reasons.
Preferably, the distance between adjacent stabilizers remains constant.
Preferably, a plurality of stabilizing devices are arranged in the condensation end, and the distance between the stabilizing devices is increased from the inlet of the condensation end 102 (i.e. from the position where the heat pipe 10 extends into the air channel) to the end of the condensation end 102. Let the distance from the position where the heat pipe 10 extends into the air passage be H, and the spacing between adjacent stabilizers be S, S ═ F1(H) I.e. S is a function of the height H as a variable, S' is the first derivative of S, satisfying the following requirements:
S’>0；
the main reason is that the steam in the condensation end is continuously condensed in the rising process, and the steam is continuously less and less, so that the steam in the gas-liquid two-phase flow is less and less, and the steam phase in the gas-liquid two-phase flow is less and less. The distance between adjacent stabilizers to be set is therefore longer and longer, so that further cost savings can be achieved, substantially the same effect can be achieved, and the flow resistance can be reduced.
Through the experiment discovery, through foretell setting, both can reduce vibrations and noise to the at utmost, can improve the heat transfer effect simultaneously.
It is further preferred that the distance between adjacent stabilizers increases from the entrance of the condensation end 102 (i.e., from the point where the heat pipe 10 extends into the air channel) to the end of the condensation end 102. I.e. S "is the second derivative of S, the following requirements are met:
S”>0；
through the experiment discovery, through so setting up, can further reduce the resistance about 7%, reach basically the same heat transfer effect simultaneously.
Preferably, a plurality of stabilizing devices are arranged in the condensation end 102, and the side length of the square is larger and larger from the inlet of the condensation end 102 (i.e. from the position where the heat pipe 10 extends into the air channel) to the end of the condensation end 102. Let the distance from the position where the heat pipe 10 extends into the water tank be H, the side length of the square be C, C ═ F2(H) And C' is the first derivative of C, and meets the following requirements:
C’>0；
it is further preferred that the side length of the square increases continuously from the lower end of the heat pipe upwards at the condensation end 102. C' is the second derivative of C, and meets the following requirements:
C”>0。
see the previous variation in the pitch of the stabilizer for specific reasons.
Preferably, the distance between adjacent stabilizers remains constant.
Through analysis and experiments, the distance between the stabilizing devices cannot be too large, the damping, noise reduction and separation effects are poor if the distance is too large, meanwhile, the distance cannot be too small, the resistance is too large if the distance is too small, and similarly, the side length of a square cannot be too large or too small, the damping and noise reduction effects are poor or the resistance is too large, so that the damping and noise reduction effects are optimized under the condition that normal flow resistance (the total pressure bearing is less than 2.5MPa or the on-way resistance of a single heat pipe is less than or equal to 5Pa/M) is preferentially met through a large number of experiments, and the optimal relation of each parameter is arranged.
Preferably, the invention is arranged on a vertical flue. The heat pipe and the extending direction of the flue form a certain angle. I.e. the heat pipe is at an angle to the horizontal.
Preferably, the distance between adjacent stabilizers is K1, the side length of the square through hole is B1, the heat pipe is a square section, the side length of the square section of the heat pipe is B2, and an acute angle formed by the heat pipe and the horizontal plane is A, so that the following requirements are met:
c*K1/B2＝a*Ln(B1/B2)+b
wherein a, b are parameters, wherein 1.725<a<1.733,4.99<b<5.01；c＝1/cos(A)mWherein 0.085<m<0.095, preferably m ═ 0.090.
11<B2<46mm；
1.9<B1<3.2mm；
18<K1<27mm。
0°<A<50°。
Preferably, 0 ° < a <25 °.
Further preferably, a is smaller and B is larger as B1/B2 is increased.
Preferably, a is 1.728, b is 4.997;
preferably, the side length B1 of the square through hole is the average of the inner side length and the outer side length of the square through hole, and the side length B2 of the square cross section of the heat pipe is the average of the inner side length and the outer side length of the heat pipe.
Preferably, the outer length of the square through hole is equal to the inner length of the square section of the heat pipe.
As a increases, m becomes smaller.
Preferably, as B2 increases, B1 also increases. However, as B2 increases, the magnitude of the increase in B1 becomes smaller and smaller. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect and the noise are further improved and reduced through the change of the rule.
Preferably, K1 decreases as B2 increases. However, as B2 increases, K1 decreases by a lesser and lesser amount. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect and the noise are further improved and reduced through the change of the rule.
Learn through analysis and experiment, the interval of heat pipe also satisfies certain requirement, for example can not too big or undersize, no matter too big or undersize can lead to the heat transfer effect not good, because set up stabilising arrangement in this application heat pipe moreover, consequently stabilising arrangement also has certain requirement to the heat pipe interval. Therefore, through a large number of experiments, under the condition that the normal flow resistance (the total pressure bearing is less than 2.5MPa, or the on-way resistance of a single heat pipe is less than or equal to 5Pa/M) is preferentially met, the damping and noise reduction are optimized, and the optimal relation of each parameter is arranged.
The distance between adjacent stabilizing devices is K1, the side length of a square is B1, the heat pipe is a square section, the side length of the heat pipe is B2, an acute angle formed by the heat pipe and a horizontal plane is A, and the distance between the centers of the adjacent heat pipes is K2, so that the following requirements are met:
c*K2/B2＝d*(K1/B2)2+e-f*(K1/B2)3-h*(K1/B2)；
wherein d, e, f, h are parameters,
1.239<d<1.240,1.544<e<1.545,0.37<f<0.38,0.991<h<0.992；c＝1/cos(A)nwherein 0.090<n<0.098, preferably n ═ 0.093.
11<B2<46mm；
1.9<B1<3.2mm；
18<K1<27mm。
16<K2<76mm。
The spacing K2 between the centers of adjacent heat pipes refers to the distance between the heat pipe centerlines.
As a increases, n becomes smaller.
0°<A<50°。
Preferably, 0 ° < a <25 °.
Further preferably, d is 1.2393, e is 1.5445, f is 0.3722, h is 0.9912;
preferably, d, e, f are larger and h is smaller as K1/B2 is increased.
Preferably, K2 increases with increasing B2, but K2 increases with increasing B2 to a lesser and lesser extent. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect can be further improved through the change of the rule.
Preferably, the length of the evaporation end (the length of the heat pipe in the flue 1) is between 1000 and 1800 mm. More preferably, 1200-1400 mm.
Preferably, the length of the condensation end is between 500 and 900 mm. More preferably, 600-700 mm.
By optimizing the optimal geometric dimension of the formula, the optimal effect of shock absorption and noise reduction can be achieved under the condition of meeting the normal flow resistance.
For other parameters, such as pipe wall, wall thickness, etc., it is sufficient to set the parameters according to normal standards.
The heat pipes are multiple, and the distribution density of the heat pipes is smaller and smaller along the flowing direction of the flue gas. In numerical simulation and experiments, the heat pipes are heated less and less along the flowing direction of the flue gas, and the temperatures of the heat pipes at different positions are different, so that local heating is not uniform. Because the temperature of the flue gas is continuously reduced along with the continuous heat exchange of the flue gas, the heat exchange capacity is also reduced, and therefore, the density of the heat pipes arranged at different positions of the flue gas channel is different, the heat absorption capacity of the heat pipes is continuously reduced along the flow direction of the flue gas, the temperature of the whole heat pipes is basically the same, the whole heat exchange efficiency is improved, materials are saved, the local damage caused by uneven temperature is avoided, and the service life of the heat pipes is prolonged.
Preferably, the distribution density of the heat pipes is continuously increased with smaller and smaller amplitude along the flow direction of the flue gas. As the change of the distribution density of the heat pipe, the invention carries out a large number of numerical simulations and experiments, thereby obtaining the change rule of the distribution density of the heat pipe. Through the change rule, materials can be saved, and meanwhile, the heat exchange efficiency can be improved by about 9%.
Preferably, the diameter and length of each heat pipe 10 are the same.
Preferably, the length of the flue in which the heat pipes are distributed along the flow direction of the flue gas is C, and the density of the heat pipes 10 at the tail part of the rearmost end of the flue along the flow direction of the flue gas is MTailThen, the density M of the heat pipe at the position l away from the tail of the heat pipe 10 is as follows: m ═ b ═ MTail+c*MTail*(l/C)aWherein a, b and c are coefficients, and the following requirements are met:
1.083<a<1.127,0.982<b+c<1.019，0.483<b<0.648。
preferably, a gradually decreases as l/C increases.
Preferably, 1.09< a <1.11, b + c ═ 1, 0.543< b < 0.578;
the optimized formula is obtained through a large number of experiments and numerical simulation, the distribution density of the heat pipes can achieve optimized distribution, the heat distribution can be uniform on the whole, the heat exchange effect is good, and meanwhile materials can be saved. Preferably, the vertical portion 101 is provided in the air passage. By heating the air channel, the heated air is directly used for combustion.
Preferably, the number of the heat pipes is multiple, and the pipe diameter of the heat pipe is smaller and smaller along the flowing direction of the flue gas. In numerical simulation and experiments, the heat pipes are heated less and less along the flowing direction of the flue gas, and the temperatures of the heat pipes at different positions are different, so that local heating is not uniform. Because the temperature of the flue gas is continuously reduced along with the continuous heat exchange of the flue gas, the heat exchange capacity is also reduced, and therefore, the heat absorption capacity of the heat pipes is continuously reduced along the flow direction of the flue gas by arranging the heat pipes with different pipe diameters at different positions of the flue gas channel, so that the temperature of the whole heat pipes is basically the same, the whole heat exchange efficiency is improved, materials are saved, the local damage caused by uneven temperature is avoided, and the service life of the heat pipes is prolonged.
Preferably, the pipe diameter of the heat pipe is gradually increased along the flowing direction of the flue gas in a smaller and smaller range. As the change of the pipe diameter of the heat pipe, the invention carries out a large number of numerical simulations and experiments, thereby obtaining the change rule of the pipe diameter of the heat pipe. Through the change rule, materials can be saved, and meanwhile, the heat exchange efficiency can be improved by about 8%.
Preferably, the distribution density and length of all heat pipes 10 are the same.
The length of the flue of the heat pipe is C along the flowing direction of the flue gas, and the flue is the last along the flowing direction of the flue gasThe diameter of the heat pipe at the end, i.e. the tail of the heat pipe, is DTailThen, the rule of the pipe diameter D of the heat pipe at the position l away from the tail of the heat pipe is as follows:
D2＝b*(Dtail)2+c*(DTail)2*(l/C)aWherein a, b and c are coefficients, and the following requirements are met:
1.085<a<1.125,0.985<b+c<1.015，0.485<b<0.645。
preferably, a gradually decreases as l/C increases.
Preferably, 1.093< a <1.106, b + c ═ 1, 0.548< b < 0.573;
the optimized formula is obtained through a large number of experiments and numerical simulation, the distribution density of the heat pipes can achieve optimized distribution, the heat distribution can be uniform on the whole, the heat exchange effect is good, and meanwhile materials can be saved.
Preferably, the length of the condensation end extending to the air channel in the flow direction of the flue gas is smaller and smaller.
Preferably, the length of the condensation end extending to the air passage along the flowing direction of the flue gas is increased in a smaller and smaller range. The change of the above-mentioned law is similar with the change of the preceding distribution density diameter, all is along the flow direction of flue gas, reduces heat transfer area for along flue gas flow direction, the heat absorbing capacity of condenser pipe constantly descends, with the decline gradually that is suitable for heat transfer quantity.
Further preferably, as shown in fig. 1, the waste heat utilization system comprises a heat reservoir 2, and the flue gas channel comprises a main pipe 12 and a secondary pipe 13. The heat pipes are arranged on the main duct 12 of the flue. The heat reservoir 2 is arranged on the auxiliary pipeline 13, and the main pipeline 12 and the auxiliary pipeline 12 form a parallel pipeline. Flue gas in the flue 14 respectively enters the air preheater 1 and the heat reservoir 2 of the main pipeline 12 and the auxiliary pipeline 13, air is heated through heat pipes, heat is stored in the heat reservoir 2, and the flue gas after heat exchange in the air preheater 1 and the heat reservoir 2 is converged and enters the main flue.
In the system, the air is heated by the waste heat of the flue gas, and the heat storage can be carried out by using the heat storage device.
As shown in fig. 1, the system comprises a heat reservoir valve 17 and an air preheater valve 5, an upstream valve 6 and a downstream valve 7, the upstream valve 6 being arranged on the flue 14 upstream of the air preheater 1 and the heat reservoir 2, for controlling the total flue gas flow into the air preheater 1 and the heat reservoir 2, a downstream valve 7 is arranged on the flue 14 downstream of the air preheater 1 and the heat reservoir 2, an air preheater valve 5 is arranged at the position of the inlet of the air preheater 1 of the main flue 12, for controlling the flow of flue gas entering the air preheater 1, a heat reservoir valve 17 is arranged at the location of the inlet pipe of the heat reservoir 2 of the secondary conduit 13, the system is used for controlling the flow of flue gas entering the heat reservoir 2, and further comprises a central controller which is in communication data connection with the heat reservoir valve 17, the air preheater valve 5, the upstream valve 6 and the downstream valve 7. The central controller controls the opening and closing of the heat reservoir valve 17, the air preheater valve 5, the upstream valve 6 and the downstream valve 7 and the opening degree, so that the smoke volume entering the air preheater 1 and the heat reservoir 2 is controlled.
Preferably, as shown in fig. 8, the system is further provided with a bypass pipeline connected with the flue 14, the connection position of the bypass pipeline and the flue 14 is positioned at the upstream of the upstream valve 6, and the bypass pipeline is provided with a bypass valve 15. The bypass valve 15 is in data connection with the central control unit 3. The opening and closing of the bypass valve 15 can ensure whether the flue gas passes through the air preheater 1 and the heat reservoir 2.
Preferably, the bypass valve 15 is open and the upstream valve 6 and the downstream valve 7 are closed.
Controlling the opening and closing of the valve according to the flow of the smoke
Preferably, a flue gas sensor is arranged in the flue 14 upstream of the upstream valve 6, and the flue gas sensor is used for detecting whether flue gas flows through the flue. The flue gas sensor is in data connection with a central controller, and the central controller controls the opening and closing of the upstream valve 6 and the downstream valve according to data detected by the flue gas sensor.
When the central controller detects that flue gas passes through the flue 14, for example, when the boiler is in operation, the central controller controls the upstream valve 6 and the downstream valve 7 to be in an open state, the flue gas can enter the air preheater 1 and the heat reservoir 2, and the flue gas is exhausted after heat exchange is completed. When the central controller detects that no smoke passes through the flue 14, for example, when the boiler stops running, the central controller controls the upstream valve 6 and the downstream valve 7 to be closed, and the pipelines in which the air preheater 1 and the heat reservoir 2 are located form a circulating pipeline. At this time, the air preheater 1 is heated by the heat stored in the heat reservoir 2, thereby preheating the air. Through the operation, when smoke exists, under the condition that the preheated air quantity generated by the air preheater 1 is met, more heat can be stored in the heat reservoir 2, and under the condition that no smoke waste heat exists, the air preheater 1 is heated by utilizing the heat stored by the smoke waste heat, so that the actual working requirement of the air preheater 1 is met. Therefore, the waste heat of the flue gas can be fully utilized, and the waste of excessive heat is avoided.
Preferably, the bypass valve 15 is open and the upstream valve 6 and the downstream valve 7 are closed.
Preferably, when the smoke sensor detects smoke, the central controller controls the bypass valve 15 to close and the upstream valve 6 and the downstream valve 7 to open.
Preferably, when the smoke sensor detects the absence of smoke, the central controller controls the bypass valve 15 to open and the upstream valve 6 and the downstream valve 7 to close.
(II) controlling the operation of the fan of the closed circulation system according to the flow of the flue gas
Preferably, a fan is arranged on the secondary pipeline 13, and the upstream valve 6 and the lower valve 7 are closed under the condition that no residual heat of flue gas exists, so that the pipelines where the air preheater 1 and the heat reservoir 2 are located form a circulating pipeline through the operation of the fan.
Preferably, the fan is in data connection with a central controller, and the central controller 3 automatically controls the operation of the fan according to data monitored by a flue sensor.
When the central controller detects that smoke passes through the pipeline, the central controller automatically controls the fan to stop running. When the central controller detects that no smoke passes through the pipeline, the central controller automatically controls the fan to start running. By controlling the intelligent operation of the fan, the intelligent control of the operation of the fan can be realized according to the actual condition, and the intelligence of the system is improved.
(III) controlling the operation of the fan according to the double temperature detection
Preferably, a first temperature sensor is arranged in the heat reservoir 2 and is used for detecting the temperature of the heat storage material in the heat reservoir. And a second temperature sensor is arranged in the air preheater and used for detecting the temperature of the air in the air preheater 1. The first temperature sensor and the second temperature sensor are in data connection with the central controller 3. The upstream valve 6 and the lower valve 7 are closed, and the central controller 3 automatically controls the operation of the fan according to the temperatures detected by the first temperature sensor and the second temperature sensor.
If the temperature detected by the first temperature sensor is lower than the temperature detected by the second temperature sensor, the central controller 3 controls the fan to stop operating. If the temperature detected by the first temperature sensor is higher than the temperature detected by the second temperature sensor, the central controller 3 controls the fan to start operating.
The operation of the fan is controlled through the detected temperature, and the air preheater can be automatically heated. Since it was found in the course of research and development and experiments that the temperature of the gas from the heat reservoir is lower than the temperature of the air in the air preheater 1 when the heat of the heat reservoir is gradually used up, it is impossible to heat the air preheater by using the heat reservoir, and the heat of the air preheater may be taken away. Therefore, the operation of the fan is intelligently controlled according to the detected temperature, so that the circulation of the heat reservoir 2 and the air preheater 1 is intelligently controlled, and the air preheating effect is improved.
(IV) controlling the opening of the valve according to the temperature of the flue gas at the inlet of the air preheater
Preferably, a third temperature sensor is provided at the location of the flue gas inlet of the air preheater 1 for measuring the temperature of the flue gas entering the air preheater. The third temperature sensor is in data connection with the central controller 3, and the central controller automatically controls the valve opening degrees of the air preheater valve 5 and the heat reservoir valve 17 according to the temperature detected by the third temperature sensor.
Preferably, when the temperature measured by the third temperature sensor is lower than a certain temperature, the central controller controls the valve 5 to increase the opening degree, and controls the valve 17 to decrease the opening degree, so as to increase the flow rate of the flue gas entering the air preheater 1. When the temperature measured by the third temperature sensor is higher than a certain temperature, the central controller controls the valve 5 to decrease the opening degree, and simultaneously controls the valve 17 to increase the opening degree, so as to decrease the flow rate of the air entering the air preheater 1.
When the temperature measured by the third temperature sensor is low to a certain temperature, the air preheating capacity of the air preheater 1 is poor, and normal requirements cannot be met, so that more smoke is needed to heat the air preheater, and the air is preheated.
Through foretell operation, can be when flue gas temperature is high, after satisfying the air demand that preheats, carry out the heat-retaining with unnecessary heat through the heat reservoir, when flue gas temperature is low, can be used for preheating the air in getting into air heater with more flue gases, guaranteed the demand of the air of preheating, simultaneously the energy saving.
(V) controlling the opening and closing of the valve according to the temperature of the flue gas
Preferably, a fourth temperature sensor is arranged in the flue 14 upstream of the upstream valve 6, and the fourth temperature sensor is used for detecting the temperature of the flue gas in the flue. The fourth temperature sensor is in data connection with the central controller, and the central controller controls the opening and closing of the upstream valve 6 and the downstream valve 7 according to data detected by the fourth temperature sensor.
When the central controller detects that the temperature of the flue 14 exceeds a certain temperature, for example, the boiler starts to discharge high-temperature flue gas when operating, the central controller controls the upstream valve 6 and the downstream valve 7 to be in an open state, the flue gas can enter the air preheater 1 and the heat reservoir 2, and the flue gas is discharged after heat exchange is completed. When the central controller detects that the flue gas temperature of the flue 14 is lower than a certain temperature, for example, when the boiler stops operating, or because the flue gas temperature is lower due to the utilization of the waste heat in the front, in order to avoid low-temperature corrosion or incapability of utilizing the waste heat, the central controller controls the upstream valve 6 and the downstream valve 7 to be closed, and the pipelines where the air preheater 1 and the heat reservoir 2 are located form a circulating pipeline. At this time, the air preheater 1 is heated by the heat stored in the heat reservoir 2, thereby preheating the air. Through the operation, when the flue gas temperature meets the requirement, under the condition of meeting the preheated air quantity generated by the air preheater 1, the excessive heat is stored in the heat reservoir 2, and under the condition of no flue gas waste heat, the heat stored by the flue gas waste heat is utilized to heat the air preheater 1 so as to meet the actual working requirement of the air preheater 1. Therefore, the waste heat of the flue gas can be fully utilized, and the waste of excessive heat is avoided.
Preferably, when the smoke sensor detects that a certain temperature is exceeded, the central controller controls the bypass valve 15 to close and the upstream valve 6 and the downstream valve 7 to open.
Preferably, when the smoke sensor detects that the temperature is lower than a certain temperature, the central controller controls the bypass valve 15 to be opened, and the upstream valve 6 and the downstream valve 7 to be closed.
(VI) controlling the operation of the fan of the closed circulation system according to the flow of the flue gas
This embodiment is an improvement on the basis of the (fifth) embodiment.
Preferably, a fan is arranged on the secondary pipeline 13, and when the temperature of the flue gas in the pipeline 14 is lower than a certain temperature, the pipelines where the air preheater 1 and the heat reservoir 2 are located form a circulation pipeline through the operation of the fan.
Preferably, the fan is in data connection with a central controller, and the central controller 3 automatically controls the operation of the fan according to data monitored by a flue sensor.
When the central controller detects that the temperature of the flue gas in the pipeline is higher than a certain temperature, the central controller controls the upstream valve 6 and the downstream valve 7 to be opened, and the fan is automatically controlled to stop running. Because the flue gas temperature at this moment satisfies the heat transfer needs, consequently can utilize the flue gas to heat air heater and heat reservoir 2. When the central controller detects that the temperature of the flue gas in the pipeline is lower than a certain temperature, the central controller controls the upstream valve 6 and the downstream valve 7 to be closed, and the central controller automatically controls the fan to start running. Because the flue gas temperature does not meet the heat exchange requirement at this moment, the heat reservoir 2 is required to be used for heating the air preheater. Through the intelligent operation according to flue gas temperature control fan, can realize the intelligent control of fan operation according to actual conditions, improve the intellectuality of system.
When the central controller detects that the temperature of the flue gas in the pipeline is higher than a certain temperature, the bypass valve is closed. When the central controller detects that the temperature of the flue gas in the pipeline is lower than a certain temperature, the bypass valve is opened.
Seventhly, the operation of the fan is controlled according to the detection of the outlet temperature of the heat reservoir
Preferably, a first temperature sensor is arranged at the outlet of the heat reservoir 2 for detecting the temperature of the gas at the outlet of the heat reservoir. And a second temperature sensor is arranged in the air preheater and used for detecting the temperature of the air in the air preheater 1. The first temperature sensor and the second temperature sensor are in data connection with the central controller 3. The central controller 3 automatically controls the operation of the fan according to the temperatures detected by the first temperature sensor and the second temperature sensor.
If the temperature detected by the first temperature sensor is lower than the temperature detected by the second temperature sensor, the central controller 3 controls the fan to stop operating.
Under the condition that upstream valve and downstream valve are closed, the operation of fan is controlled through the temperature that detects, can realize independently heating air heater. Since it was found in the course of research and development and experiments that the temperature of the gas from the heat reservoir is lower than the temperature of the air in the air preheater 1 when the heat of the heat reservoir is gradually used up, it is impossible to heat the air preheater by using the heat reservoir, and the heat of the air preheater may be taken away. Therefore, the operation of the fan is intelligently controlled according to the detected temperature, so that the circulation of the heat reservoir 2 and the air preheater 1 is intelligently controlled, and the generation rate of preheated air is improved.
Although the present invention has been described with reference to the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.

Claims (2)

1. A power station boiler waste heat utilization system comprises an air preheater and a heat reservoir, wherein the air preheater is arranged on a main pipeline of a flue, the heat reservoir is arranged on an auxiliary pipeline, the main pipeline and the auxiliary pipeline form a parallel pipeline, flue gas in the flue respectively enters the air preheater and the heat reservoir of the main pipeline and the auxiliary pipeline, air is heated in the air preheater, heat is stored in the heat reservoir, and the flue gas after heat exchange in the air preheater and the heat reservoir converges and enters the flue;
the air preheater comprises a heat pipe, a flue gas channel and an air channel, wherein the heat pipe comprises an evaporation end and a condensation end, the condensation end is arranged in the air channel, and the evaporation end is arranged in the flue; the evaporation end absorbs the waste heat of the flue gas in the boiler flue, the heat is transferred to the air in the air channel through the condensation end, and the preheated air enters the boiler hearth for supporting combustion;
a stabilizing device is arranged in the heat pipe, the stabilizing device is of a sheet structure, and the sheet structure is arranged on the cross section of the heat collecting pipe; the stabilizing device consists of a square through hole and a regular octagonal through hole, the side length of the square through hole is equal to that of the regular octagonal through hole, four sides of the square through hole are respectively sides of four different regular octagonal through holes, and four mutually spaced sides of the regular octagonal through hole are respectively sides of four different square through holes;
the system comprises an air preheater valve, a heat reservoir valve, a central controller and a third temperature sensor, wherein the air preheater valve is arranged at the position of an inlet of an air preheater of a main flue and used for controlling the flow of flue gas entering the air preheater, the heat reservoir valve is arranged at the position of an inlet pipe of a heat reservoir of an auxiliary pipeline and used for controlling the flow of the flue gas entering the heat reservoir, the central controller is in data connection with the air preheater valve and the heat reservoir valve, and the third temperature sensor is arranged at the position of the flue gas inlet of the air preheater and used for measuring the temperature of the flue gas entering the air preheater; the third temperature sensor is in data connection with the central controller, and the central controller automatically controls the valve opening degrees of the air preheater valve and the heat reservoir valve according to the temperature detected by the third temperature sensor.
2. The waste heat utilization system as claimed in claim 1, wherein when the temperature measured by the third temperature sensor is lower than a certain temperature, the central controller controls the air preheater valve to be opened more, and controls the heat reservoir valve to be opened less, so as to increase the flow rate of the flue gas entering the air preheater; when the temperature measured by the third temperature sensor is higher than a certain temperature, the central controller controls the valve of the air preheater to reduce the opening degree, and controls the valve of the heat reservoir to increase the opening degree simultaneously so as to reduce the flow of the flue gas entering the air preheater.
CN201810819057.2A 2018-07-24 2018-07-24 Power station boiler waste heat utilization system based on inlet flue gas temperature communication control Active CN110529872B (en)

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CN113465423B (en) * 2020-07-23 2022-04-15 中北大学 Flue gas monitoring heat pipe system
CN113137621B (en) * 2020-10-14 2022-02-08 山东大学 Flue distributor utilizing heat pipe for temperature equalization
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