CN209495348U - Hot Secondary Air and smoke waste heat utilization system and thermal power generation unit - Google Patents
Hot Secondary Air and smoke waste heat utilization system and thermal power generation unit Download PDFInfo
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- CN209495348U CN209495348U CN201920193697.7U CN201920193697U CN209495348U CN 209495348 U CN209495348 U CN 209495348U CN 201920193697 U CN201920193697 U CN 201920193697U CN 209495348 U CN209495348 U CN 209495348U
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- 239000002918 waste heat Substances 0.000 title claims abstract description 52
- 238000010248 power generation Methods 0.000 title abstract description 11
- 239000000779 smoke Substances 0.000 title abstract description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 252
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims abstract description 153
- 239000003546 flue gas Substances 0.000 claims abstract description 153
- 238000010521 absorption reaction Methods 0.000 claims abstract description 40
- 239000000428 dust Substances 0.000 claims description 42
- 238000010438 heat treatment Methods 0.000 claims description 16
- 239000004071 soot Substances 0.000 abstract description 8
- 238000009833 condensation Methods 0.000 abstract description 4
- 230000005494 condensation Effects 0.000 abstract description 4
- 238000004140 cleaning Methods 0.000 abstract description 2
- 239000003517 fume Substances 0.000 abstract 2
- 239000003245 coal Substances 0.000 description 15
- 230000001965 increasing effect Effects 0.000 description 14
- 238000005260 corrosion Methods 0.000 description 13
- 230000007797 corrosion Effects 0.000 description 13
- 238000005299 abrasion Methods 0.000 description 10
- 238000006477 desulfuration reaction Methods 0.000 description 9
- 230000023556 desulfurization Effects 0.000 description 9
- 239000007789 gas Substances 0.000 description 8
- 230000001976 improved effect Effects 0.000 description 8
- 230000001939 inductive effect Effects 0.000 description 8
- 239000000463 material Substances 0.000 description 7
- 230000008901 benefit Effects 0.000 description 6
- 238000007664 blowing Methods 0.000 description 6
- 239000003344 environmental pollutant Substances 0.000 description 6
- 231100000719 pollutant Toxicity 0.000 description 6
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000005265 energy consumption Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 4
- 238000000605 extraction Methods 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- RAHZWNYVWXNFOC-UHFFFAOYSA-N Sulphur dioxide Chemical compound O=S=O RAHZWNYVWXNFOC-UHFFFAOYSA-N 0.000 description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 description 2
- 239000001569 carbon dioxide Substances 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000746 purification Methods 0.000 description 2
- 238000003303 reheating Methods 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 239000002253 acid Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000009835 boiling Methods 0.000 description 1
- 239000003518 caustics Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000003009 desulfurizing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
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- 239000000284 extract Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 150000003568 thioethers Chemical class 0.000 description 1
Classifications
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
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- Air Supply (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The utility model belongs to fume afterheat using technical field, is related to a kind of hot Secondary Air and smoke waste heat utilization system and thermal power generation unit.The hot Secondary Air and smoke waste heat utilization system of the utility model, including air preheater, deduster, absorption tower, hot Secondary Air-water supply/condensation water- to-water heat exchanger and flue gas-air heat exchanger；The hot Secondary Air outlet of air preheater connects hot Secondary Air bypass, and hot Secondary Air bypass is connect with hot Secondary Air-water supply/condensation water- to-water heat exchanger, and water supply/condensed water is heated using hot Secondary Air；Flue gas-air heat exchanger is arranged in the inlet of deduster, heats cold wind using the low-temperature flue gas of deduster entrance；Alternatively, flue gas-air heat exchanger is arranged in the inlet on absorption tower, cold wind is heated using the low-temperature flue gas of absorption tower entrance.The utility model fume afterheat utilization rate is high, have the characteristics that cleaning, without wear, it is corrosion-free, soot blower system that no setting is required, equipment cost is low, safe and reliable to operation.
Description
Technical Field
The utility model belongs to the technical field of flue gas waste heat utilization, particularly, relate to a hot overgrate air and flue gas waste heat utilization system and thermal generator set.
Background
At present, the power generation form in China still mainly uses coal power, and the coal power is used as the main body of the power production in China, so that the development space is still large. Coal is a large carbon dioxide emission source in China, and coal power enterprises are large carbon dioxide emission enterprises. At present, the most effective and realistic emission reduction method is to improve the power generation efficiency, so that the high-efficiency and clean coal-electricity technology is the main direction for future development. The discharge amount of pollutants is related to the coal consumption of the thermal power plant, and reducing the discharge amount of pollutants from the thermal power plant to the atmosphere while reducing the coal consumption of the thermal power plant is a promising technology. With the improvement of environmental protection requirements, how to further improve the efficiency of the unit and reduce energy consumption is an important subject to which people face.
Generally speaking, the improvement of unit efficiency and the reduction of energy consumption mainly can be started from the aspects of improving steam parameters and reducing heat loss. And (one) increasing steam parameters, including increasing the pressure and temperature of the steam. The steam parameters of the thermal power plant are gradually increased from subcritical parameters to supercritical parameters, and further increased to ultra supercritical parameters. In recent years, the ultra-supercritical secondary reheating technology has become a product which is mainly developed in China. The secondary reheating unit not only can enable the power station unit to obtain higher economical efficiency, but also can enable the unit to have better environmental protection effect, and is a mature, efficient and low-pollution coal-fired power generation technology. Along with the improvement of steam temperature and pressure of a thermal power plant, the efficiency of a steam turbine is improved, heat consumption is reduced, the efficiency of the whole thermal power generation system can be improved, and coal consumption is reduced. And (II) reducing heat loss, including reducing steam turbine exhaust parameters and boiler exhaust heat loss. The magnitude of the decrease in the steam discharge parameters is limited by the temperature of the circulating cooling water of the power plant. The boiler exhaust heat loss is the most important heat loss in the operation of the boiler, generally accounts for 5% -12% of the boiler heat loss, accounts for 60% -70% of the boiler heat loss, and the main factor influencing the exhaust heat loss is the exhaust temperature. Generally, the exhaust gas temperature is between 110 ℃ and 170 ℃ according to different boiler forms and different types of fire coal, so that the reduction of the exhaust gas temperature has important significance for saving the coal consumption and reducing pollutants.
The flue gas waste heat utilization system is an effective means for reducing the heat loss of flue gas emission of a power plant and realizing the utilization of flue gas waste heat. The waste heat of the flue gas is generally used for exchanging the heat in the flue gas to other media through a flue gas heat exchanger for utilization. For example, an existing high-efficiency replacement type flue gas waste heat utilization system, namely an economizer system of an air preheater bypass, is provided with an air preheater bypass flue, and flue gas with higher temperature is used for heating condensate water or feed water with higher temperature of a steam turbine, so that higher power generation benefit is obtained, and the temperature of the flue gas entering an absorption tower is reduced. The coal economizer system of the existing air preheater bypass can efficiently utilize the waste heat of boiler flue gas, but because the flue gas dust content of the bypass is high and has certain corrosivity, the problems of abrasion resistance and corrosion resistance need to be considered, certain risks exist, a complex soot blowing system and complex soot blowing equipment need to be arranged, the equipment cost is high, the system is relatively complex, the flue gas heat exchanger is easy to wear, and the safe operation of a unit is influenced.
In view of this, the utility model is especially provided.
SUMMERY OF THE UTILITY MODEL
A first object of the utility model is to provide a hot overgrate air and flue gas waste heat utilization system, flue gas waste heat utilization rate is high, has characteristics such as clean, no wearing and tearing, no corruption, need not to set up soot blower system, and equipment cost is low, and operation safe and reliable can overcome above-mentioned problem or solve above-mentioned technical problem at least partially.
A second object of the utility model is to provide a thermal generator set, this thermal generator set include foretell hot overgrate air and flue gas waste heat utilization system, have unit efficiency height, the energy consumption is low, flue gas waste heat utilization rate is high, has reduced pollutant discharge and has practiced thrift characteristics such as equipment cost.
In order to achieve the above object, the utility model adopts the following technical scheme:
according to one aspect of the present invention, the present invention provides a hot overgrate air and flue gas waste heat utilization system, the system comprising an air preheater, a dust remover, an absorption tower, a hot overgrate air-feed water/condensate water heat exchanger and a flue gas-air heat exchanger;
a hot secondary air outlet of the air preheater is connected with a hot secondary air bypass, the hot secondary air bypass is connected with the hot secondary air-water supply/condensed water heat exchanger, and the hot secondary air is used for heating the water supply/condensed water;
the flue gas-air heat exchanger is arranged at the inlet of the dust remover, and the cold air is heated by using the low-temperature flue gas at the inlet of the dust remover; or,
the flue gas-air heat exchanger is arranged at the inlet of the absorption tower, and the cold air is heated by using the low-temperature flue gas at the inlet of the absorption tower.
As a further preferred technical scheme, the air preheater is provided with a flue gas inlet, a primary cold air inlet, a secondary cold air inlet, a flue gas outlet and a hot secondary air outlet;
the flue gas inlet is connected with a flue gas outlet of a boiler furnace, the flue gas outlet is connected with an inlet of a flue gas-air heat exchanger, or the flue gas outlet is connected with an inlet of a dust remover;
the primary cold air inlet is connected with a primary fan;
the secondary cold air inlet is connected with an outlet of the hot secondary air-water supply/condensed water heat exchanger and/or an outlet of the flue gas-air heat exchanger;
the hot secondary air outlet is connected with the inlet of the hot secondary air-water supply/condensed water heat exchanger through a hot secondary air bypass.
As a further preferred technical scheme, a bypass secondary fan is arranged on an outlet connecting pipeline of the hot secondary air-water supply/condensed water heat exchanger;
the flue gas-air heat exchanger is connected with the blower, and air is heated by the flue gas-air heat exchanger, then is discharged from an outlet of the flue gas-air heat exchanger, is mixed with bypass secondary air led out by the bypass secondary fan, and enters the air preheater through a secondary cold air inlet of the air preheater.
As a further preferable technical solution, the heat exchange medium in the hot overfire air-feedwater/condensate heat exchanger includes feedwater and/or condensate, and the feedwater and/or condensate is feedwater and/or condensate in a turbine thermodynamic system.
As a further preferred technical solution, the feed water is from the outlet of a certain stage of high-pressure heater or the sum of the outlets of several stages of high-pressure heaters of a turbine feed water system;
and/or the condensed water is derived from a certain stage of low-pressure heater outlet or a plurality of stages of low-pressure heater outlets of the turbine condensed water system.
As a further preferable technical scheme, the water supply flow is full flow or partial flow, when the water supply is full flow, the heat exchanger of the hot secondary air-water supply/condensed water is connected in series with the high-pressure heater, and when the water supply is partial flow, the heat exchanger of the hot secondary air-water supply/condensed water is connected in parallel with the high-pressure heater;
and/or the condensed water is full flow or partial flow, when the condensed water is full flow, the hot secondary air-water supply/condensed water heat exchanger is connected with the low-pressure heater in series, and when the condensed water is partial flow, the hot secondary air-water supply/condensed water heat exchanger is connected with the low-pressure heater in parallel.
As a further preferable technical scheme, an intermediate medium is arranged in the flue gas-air heat exchanger, and the low-temperature flue gas and the air exchange heat through the intermediate medium.
As a further preferred technical scheme, the hot secondary air-feed water/condensed water heat exchanger is a heat pipe type heat exchanger or a surface type heat exchanger;
and/or the flue gas-air heat exchanger is a heat pipe type heat exchanger or a surface type heat exchanger.
As a further preferable technical scheme, a hot secondary air quantity adjusting device and/or a hot secondary air temperature adjusting device are/is arranged on the hot secondary air bypass;
preferably, the system further comprises an air inducing device disposed between the dust remover and the absorption tower.
According to the utility model discloses a further aspect, the utility model discloses still provide a thermal generator set, including above hot overgrate air and flue gas waste heat utilization system.
Compared with the prior art, the beneficial effects of the utility model reside in that:
1. the utility model provides a hot overgrate air and flue gas waste heat utilization system, the low temperature flue gas of make full use of air heater export heats cold wind to utilize air heater to replace the hot overgrate air of coming out high temperature to heat the condensate water and/or the feedwater of the higher temperature of steam turbine system, reduced the higher quality steam that the feedwater of higher temperature and condensate water need, flue gas waste heat utilization rate is high. In addition, as the bypass hot secondary air is adopted to heat the feed water and the condensed water, the device has the characteristics of cleanness, no abrasion, no corrosion and the like, a soot blowing system is not required to be arranged, abrasion resistance and corrosion resistance do not need to be considered for the heat exchanger material, and the device cost is greatly saved.
2. The utility model discloses a high-efficient replacement formula flue gas waste heat utilization system of hot overgrate air bypass sets up hot overgrate air bypass wind channel, utilizes the hot overgrate air of higher temperature to heat the feedwater and the condensate water of the higher temperature of steam turbine, has reduced the higher quality steam that feedwater and the condensate water of higher temperature need, obtains higher power generation benefit. In addition, because the hot secondary bypass air channel is arranged, the secondary air quantity entering the air preheater is increased, and in order to ensure that the temperature of the air at the outlet of the air preheater is not reduced or slightly increased and improve the efficiency of the boiler, the flue gas-air heat exchanger is arranged to heat the cold secondary air, reduce the temperature of the flue gas at the outlet of the boiler and replace the heat for the hot secondary air. The flue gas-air heat exchanger can be arranged at the inlet of the dust remover and also can be arranged at the inlet of the absorption tower.
3. Adopt the utility model discloses a behind the system, utilize the low temperature flue gas to heat cold overgrate air, the overgrate air of the high temperature that utilizes the displacement comes the feedwater and the condensate of heating the higher temperature of steam turbine system, the steam of the higher quality that is used for heating feedwater and condensate is squeezed in the displacement, above-mentioned steam has better doing work power generation ability, consequently this system can reduce the coal consumption of thermal power generating unit (thermal power generating unit) by a wide margin, and improve gas cleaning equipment's efficiency, reduce the water consumption of flue gas desulfurization tower, reduce the emission of pollutant.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the technical solutions in the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a multistage efficient displacement type flue gas waste heat utilization system in the prior art;
fig. 2 is a schematic structural view of a hot secondary air and flue gas waste heat utilization system provided by an embodiment of the present invention;
fig. 3 is a schematic structural view of another hot secondary air and flue gas waste heat utilization system provided by the embodiment of the present invention.
Icon: 1-a boiler; 2-an air preheater; 3-hot overfire air-feed water/condensate water heat exchanger; 4-flue gas-air heat exchanger; 5-bypass secondary fan; 6-a blower; 7-a primary air fan; 8-a dust remover; 9-an air inducing device; 10-an absorption column; 11-adjusting the flapper door; 12-a low pressure heater; 13-a high pressure heater; 14-a deaerator; 15-a feed pump; 16-a generator; 17-a high-pressure cylinder of the steam turbine; 18-a turbine intermediate pressure cylinder; 19-a low pressure cylinder of the steam turbine; 20-a condenser; 21-a condensate pump; 18-a turbine intermediate pressure cylinder; 19-a low pressure cylinder of the steam turbine; 20-a condenser; 21-a condensate pump; A1-NOi+1Adding the materials in a low grade; A2-NOiAdding the materials in a low grade; A3-NOi+1Adding the materials in a low grade; A4-NOi－2Adding the materials in a low grade; B1-NOi+1High grade is added; B2-NOiHigh grade is added; B3-NOi－1The step of adding is high.
Detailed Description
Embodiments of the present invention will be described in detail below with reference to embodiments and examples, but those skilled in the art will understand that the following embodiments and examples are only for illustrating the present invention and should not be construed as limiting the scope of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention. Those who do not specify the conditions are performed according to the conventional conditions or the conditions recommended by the manufacturer.
In a first aspect, there is provided in at least one embodiment a hot overfire air and flue gas waste heat utilization system, said system comprising an air preheater, a dust collector, an absorber tower, a hot overfire air-feedwater/condensate heat exchanger, and a flue gas-air heat exchanger;
a hot secondary air outlet of the air preheater is connected with a hot secondary air bypass, the hot secondary air bypass is connected with the hot secondary air-water supply/condensed water heat exchanger, and the hot secondary air is used for heating the water supply/condensed water;
the flue gas-air heat exchanger is arranged at the inlet of the dust remover, and the cold air is heated by using the low-temperature flue gas at the inlet of the dust remover; or,
the flue gas-air heat exchanger is arranged at the inlet of the absorption tower, and the cold air is heated by using the low-temperature flue gas at the inlet of the absorption tower.
It should be noted that:
herein, there is no particular limitation on the specific type of the air preheater (simply referred to as air preheater) as long as the object of the present invention is not limited; for example, a tubular preheater, a rotary preheater, etc. well known in the art can be used.
Herein, there is no particular limitation on the specific types of the dust collector and the absorption tower as long as the object of the present invention is not limited; for example, a bag house dust collector, an electrostatic dust collector, etc. well known in the art may be used.
Herein, the hot overfire air-feed water/condensed water heat exchanger may be one heat exchanger, or may be a plurality of heat exchangers connected in series, parallel, series-parallel.
Further, the "hot overfire air-feedwater/condensate heat exchanger" refers to a device for exchanging heat between the hot overfire air and feedwater/condensate, wherein the "feedwater/condensate" refers to feedwater, condensate, or both. That is, the heat exchanger may be a device for exchanging heat between hot secondary air and feed water, a device for exchanging heat between hot secondary air and condensate water, or a device for exchanging heat between hot secondary air and feed water and condensate water.
Herein, the flue gas-air heat exchanger may be one heat exchanger, or may be a plurality of heat exchangers connected in series, in parallel, or in series and parallel.
Further, the "flue gas-air heat exchanger" means a device for exchanging heat between flue gas and air (which may also be called cold air).
Herein, the boiler mainly includes a boiler device, and there is no specific limitation on the boiler device as long as the purpose of the present invention is not limited; for example, a pi-type boiler, a tower boiler, etc., which are well known in the art, may be used.
Herein, there is no particular limitation in each fan or air inducing device, and a type well known in the art, such as a centrifugal fan, an axial flow fan, etc., may be employed as long as the object of the present invention is not limited.
Unless defined or indicated otherwise, technical and scientific terms used herein have the same meaning as is familiar to those skilled in the art.
According to the utility model, according to the smoke circulation direction, the system comprises an air preheater, a dust remover and an absorption tower which are connected in series in sequence, and also comprises a hot secondary air-water supply/condensed water heat exchanger and a smoke-air heat exchanger; the air preheater is provided with a hot secondary air outlet, the hot secondary air outlet is connected with a hot secondary air bypass, the hot secondary air bypass is connected with a hot secondary air-water supply/condensed water heat exchanger, and the replaced hot secondary air is used for heating the water supply/condensed water; and a flue gas-air heat exchanger is arranged at the inlet of the dust remover or the inlet of the absorption tower, and the replaced low-temperature flue gas is used for heating cold air.
An existing economizer system with an air preheater bypass, for example, a patent with publication number CN202177093U, discloses a multi-stage high-efficiency displacement type flue gas waste heat utilization system, as shown in fig. 1, an air preheater bypass flue is provided, and flue gas with higher temperature is used to heat condensate water or feed water with higher temperature of a steam turbine, so as to obtain higher power generation benefit and reduce the temperature of flue gas entering an absorption tower.
Referring to the attached figure 1, although the flue gas-condensed water (feed water) heat exchange of the bypass of the air preheater can obtain higher flue gas waste heat utilization rate, the temperature of the hot secondary air is not greatly different from the flue gas temperature at the inlet of the air preheater, and higher-quality feed water or condensed water can be heated, so that the flue gas waste heat utilization rate equivalent to that of a bypass flue gas system can be obtained by adopting the heat exchange of the hot secondary air-feed water/condensed water. However, since the bypass flue contains a high amount of dust and contains corrosive substances such as sulfides, there are certain risks in considering abrasion resistance and corrosion resistance, and problems such as high cost and complicated system. In view of this, the utility model discloses creatively provides a hot overgrate air and flue gas waste heat utilization system utilizes the heat that the flue gas waste heat replaced hot overgrate air to heat feedwater and condensate to alleviate above-mentioned problem.
Compared with the prior art, the utility model provides a hot overgrate air and flue gas waste heat utilization system mainly has following characteristics:
(1) the replaced hot secondary air is used for heating the feed water and the condensed water, the hot secondary air is clean and free of dust, and the heat exchanger equipment does not need to consider the problems of abrasion and corrosion, so that the material selection range is wide, the wall thickness of the pipe is small, and the equipment cost is low.
(2) Although the heat exchange of the flue gas-feed water and the condensed water of the bypass of the air preheater is operated under the working condition of being higher than the acid dew point of the flue gas, the dust content of the flue gas is higher, the heat exchanger needs to consider anti-abrasion measures and needs to be provided with a soot blowing system. And the utility model discloses owing to adopt hot overgrate air-feedwater/condensate water heat transfer, there is not wearing and tearing and corrosion problem in the heat exchanger, need not set up the soot blowing system, and the operation control of system is convenient, more is favorable to the safe operation of unit.
(3) The cold end corrosion of the air preheater is a problem frequently encountered in the operation of a unit of a thermal power plant, a steam air heater or a hot air recirculation mode is mostly adopted for solving the problem in China, and the scheme is at the cost of improving the exhaust gas temperature, namely reducing the boiler efficiency. And the utility model discloses a flue gas-air heat transfer system, improved the air inlet temperature of air preheater, avoided the cold junction corrosion problems of air preheater completely, improved the efficiency of boiler and unit simultaneously.
(4) When the unit is operated under variable load, the temperature of the condensed water changes, the system control does not need to consider the corrosion problem of the heat exchanger, and the operation control is simple and convenient.
It can be seen that the utility model discloses waste heat utilization system to air preheater bypass flue gas has characteristics such as easy wearing and tearing and corruption, utilizes low temperature flue gas heating cold wind, replaces out the feedwater and the condensate water that clean high temperature hot overgrate air heated the steam turbine system higher temperature. After the system is adopted, the waste heat of the flue gas can be recovered to the maximum extent, the power can be generated with the highest efficiency, the coal consumption of a thermal power plant is reduced, the desulfurization water consumption is saved, the abrasion and the corrosion of the flue gas of the bypass flue to heat exchanger equipment can be prevented, the equipment cost is saved, the system is simple, and the operation and the control are convenient.
In a preferred embodiment, the air preheater is provided with a flue gas inlet, a primary cold air inlet, a secondary cold air inlet, a flue gas outlet and a hot secondary air outlet;
the flue gas inlet is connected with a flue gas outlet of a boiler furnace, the flue gas outlet is connected with an inlet of a flue gas-air heat exchanger, or the flue gas outlet is connected with an inlet of a dust remover;
the primary cold air inlet is connected with a primary fan;
the secondary cold air inlet is connected with an outlet of the hot secondary air-water supply/condensed water heat exchanger and/or an outlet of the flue gas-air heat exchanger;
the hot secondary air outlet is connected with the inlet of the hot secondary air-water supply/condensed water heat exchanger through a hot secondary air bypass.
In a preferred embodiment, a bypass secondary fan is arranged on an outlet connecting pipeline of the hot secondary air-feed water/condensed water heat exchanger;
the flue gas-air heat exchanger is connected with the blower, and air is heated by the flue gas-air heat exchanger, then is discharged from an outlet of the flue gas-air heat exchanger, is mixed with bypass secondary air led out by the bypass secondary fan, and enters the air preheater through a secondary cold air inlet of the air preheater.
In a preferred embodiment, the system further comprises an air inducing device disposed between the dust remover and the absorption tower.
According to the utility model, the air preheater is provided with a flue gas inlet, a primary cold air inlet, a secondary cold air inlet, a flue gas outlet and a hot secondary air outlet;
the flue gas inlet of the air preheater is connected with the flue gas outlet of the boiler hearth, the air preheater is connected with the primary fan through the primary cold air inlet, the air preheater is connected with the outlet of the hot secondary air-water supply/condensed water heat exchanger and/or the outlet of the flue gas-air heat exchanger through the secondary cold air inlet, and preferably, the air preheater is connected with the outlet of the hot secondary air-water supply/condensed water heat exchanger and the outlet of the flue gas-air heat exchanger through the secondary cold air inlet. Further speaking: the bypass secondary air fan is arranged on a gas outlet pipeline of the hot secondary air-water supply/condensed water heat exchanger, the air feeder is connected with the flue gas-air heat exchanger to provide cold air for the heat exchanger, the secondary air after heat release led out by the bypass secondary air fan is mixed with the secondary air (after heat absorption) at the outlet of the air feeder, and then the secondary air enters the air preheater through a secondary cold air inlet of the air preheater. The secondary hot air is formed after being heated by an air preheater, part of the secondary hot air is introduced into a hearth, and part of the secondary hot air is extracted to heat feed water and condensed water.
The hot secondary air outlet of the air preheater is connected with the inlet of a hot secondary air-water supply/condensed water heat exchanger through a hot secondary air bypass, in the heat exchanger, the hot secondary air exchanges heat with water supply and/or condensed water, the hot secondary air releases heat, the water supply and/or condensed water absorbs heat, and the water supply and/or condensed water is the water supply and/or condensed water in a thermodynamic system of the steam turbine. Furthermore, the feed water comes from the outlet of a certain stage of high-pressure heater of the steam turbine feed water system or the collection of the outlets of a plurality of stages of high-pressure heaters; the condensed water is from the outlet of a certain stage of low-pressure heater or the sum of the outlets of a plurality of stages of low-pressure heaters of the condensed water system of the steam turbine.
The feed water heat exchanger can be connected with the high-pressure heater in series by full-flow feed water, or can be connected with a certain stage of high-pressure heater in parallel by partial-flow feed water.
The condensed water heat exchanger can be connected with the low-pressure heater in series by the full-flow condensed water, and can also be connected with a certain stage of low-pressure heater in parallel by the partial-flow condensed water.
When the water supply and the condensed water are in full flow, the resistance of the flue gas heat exchanger and the water supply and condensed water pipelines at the inlet and the outlet of the flue gas heat exchanger is overcome by a water supply pump in a steam turbine water supply system and a condensed water pump in a condensed water system.
When the partial flow of the water supply and the condensed water is calculated, the resistance of the heat exchanger and a pipeline is overcome by checking the water supply and the condensed water, and whether a pump needs to be added for the water supply and the condensed water to return the water supply and the condensed water to the thermodynamic system of the steam turbine or not is considered.
It should be understood that the above "a certain stage" means any one stage of low pressure heater or any one stage of high pressure heater in the multi-stage low pressure heater or the multi-stage high pressure heater; the "certain stage" or "several stages" refers to any stage of low-pressure heater or any stage of high-pressure heater in the multi-stage low-pressure heater or the multi-stage high-pressure heater.
It should be noted that the meaning of the low-pressure heater and the high-pressure heater is known to those skilled in the art, and the present invention is not particularly limited thereto and will not be described in detail.
The turbine condensate system may be a part of a turbine regenerative system, but is not limited thereto, and may also be, for example, adjacent turbine system condensate, heat supply network water, power plants and other domestic water.
According to the utility model discloses, air heater's exhanst gas outlet and flue gas-air heat exchanger's flue gas entry linkage, the low temperature flue gas that comes out from air heater gets into to flue gas-air heat exchanger in, and in this heat exchanger, the low temperature flue gas carries out the heat transfer with the air, and the low temperature flue gas is exothermic, and air (cold wind) absorb heat. The cold air which absorbs heat from the flue gas-air heat exchanger enters the air preheater, and the flue gas which releases heat from the flue gas-air heat exchanger enters the dust remover and then enters the absorption tower through the induced draft device (a draught fan or a booster fan).
Similarly, when the flue gas-air heat exchanger is arranged at the inlet of the absorption tower, the low-temperature flue gas coming out of the flue gas outlet of the air preheater enters the flue gas-air heat exchanger after passing through the dust remover and the air inducing device, the low-temperature flue gas exchanges heat with the air in the heat exchanger, the low-temperature flue gas releases heat, and the air (cold air) absorbs heat. The cold air which absorbs heat from the smoke-air heat exchanger enters the air preheater again, and the smoke which releases heat from the smoke-air heat exchanger directly enters the absorption tower.
In a preferred embodiment, an intermediate medium is provided in the flue gas-air heat exchanger, and the low-temperature flue gas and the air exchange heat through the intermediate medium.
It can be understood that the flue gas-air heat exchanger is an indirect heat exchanger provided with an intermediate heat medium, the low-temperature flue gas transfers heat to the intermediate medium, and the intermediate medium transfers heat to the air. The intermediate medium is preferably a liquid medium, including water or other low boiling point liquids, such as ethylene glycol and the like.
In a preferred embodiment, the hot overfire air-feedwater/condensate heat exchanger is a heat pipe heat exchanger or a surface heat exchanger;
and/or the flue gas-air heat exchanger is a heat pipe type heat exchanger or a surface type heat exchanger.
It should be noted that the present invention has no special limitation on the specific types of the hot secondary air-water supply/condensed water heat exchange and the flue gas-air heat exchanger, as long as the purpose of the present invention is not limited. For example, the two may be independently a heat pipe heat exchanger or a surface heat exchanger, or a plate heat exchanger or a rotary heat exchanger.
In a preferred embodiment, a hot secondary air volume adjusting device and/or a hot secondary air temperature adjusting device is/are provided on the hot secondary air bypass.
It will be appreciated that an air flow regulating device, such as a damper door, may be provided in the bypass hot secondary air duct and may be used to regulate the hot secondary air flow to control the outlet hot secondary air temperature of the air preheater and the boiler flue gas temperature.
In a second aspect, in at least one embodiment, a thermal generator set is provided, which includes the above hot secondary air and flue gas waste heat utilization system.
According to the utility model discloses, this thermal generator set still can include other prior art well-known equipment such as boiler, steam turbine, generator including hot overgrate air and flue gas waste heat utilization system, the utility model discloses do not make special restriction to other equipment and relation of connection, this thermal generator set's core lies in including the utility model discloses a hot overgrate air and flue gas waste heat utilization system.
It can be understood that the utility model discloses a thermal generator set and foretell hot overgrate air and flue gas waste heat utilization system are based on same inventive concept, therefore have at least with the same advantage of the above-mentioned hot overgrate air and flue gas waste heat utilization system, the utility model discloses no longer describe herein.
The present invention will be further described with reference to the following specific embodiments and accompanying drawings.
Examples
As shown in fig. 2 and 3, a system for utilizing hot secondary air and flue gas waste heat comprises a boiler 1, an air preheater 2, a hot secondary air-feedwater/condensed water heat exchanger 3, a flue gas-air heat exchanger 4, a bypass secondary fan 5, a blower 6, a primary fan 7, a dust remover 8, an induced draft device 9, an absorption tower 10, a low-pressure heater 12 and a high-pressure heater 13;
wherein, the air preheater 2 is provided with a flue gas inlet, a primary cold air inlet, a secondary cold air inlet, a flue gas outlet and a hot secondary air outlet; a flue gas inlet of the air preheater 2 is connected with a flue gas outlet of a hearth of the boiler 1, the air preheater 2 is connected with a primary air fan 7 through a primary cold air inlet, a bypass secondary air fan 5 is arranged on a gas outlet pipeline of the hot secondary air-water supply/condensed water heat exchanger 3, an air feeder 6 is connected with the flue gas-air heat exchanger 4, secondary air which is led out by the bypass secondary air fan 5 and used for releasing heat is mixed with secondary air (used for absorbing heat) at an outlet of the air feeder 6, and then the secondary cold air is connected with a secondary cold air inlet of the air preheater 2 through a pipeline.
The hot secondary air outlet of the air preheater 2 is connected with a hot secondary air-water supply/condensed water heat exchanger 3 through a hot secondary air bypass, in the heat exchanger, the hot secondary air exchanges heat with water supply and/or condensed water, the hot secondary air releases heat, the water supply and/or the condensed water absorbs heat, and the water supply is from the outlet of a certain-stage high-pressure heater 13 of a steam turbine water supply system or the collection of the outlets of a plurality of high-pressure heaters 13; the condensed water is from the outlet of a certain stage of low-pressure heater 12 of the condensed water system of the steam turbine or the sum of the outlets of a plurality of stages of low-pressure heaters 12.
Referring to fig. 2, the flue gas outlet of the air preheater 2 is connected to the flue gas inlet of the flue gas-air heat exchanger 4, in which heat exchange is performed between low-temperature flue gas and air, the low-temperature flue gas releases heat, and the air (cold air) absorbs heat. The cold air which absorbs heat from the heat exchanger enters the air preheater 2 again, and the flue gas which releases heat from the heat exchanger enters the dust remover 8 and then enters the absorption tower 10 through the air inducing device 9.
Referring to fig. 3, a flue gas outlet of the air preheater 2 is connected with a dust remover 8, the dust remover 8 is connected with an air inducing device 9, low-temperature flue gas from the air inducing device 9 enters a flue gas-air heat exchanger 4, in the heat exchanger, the low-temperature flue gas exchanges heat with air, the low-temperature flue gas releases heat, and the air (cold air) absorbs heat. The cold air which absorbs heat from the heat exchanger enters the air preheater 2 again, and the flue gas which releases heat from the flue gas-air heat exchanger 4 directly enters the absorption tower 10.
The working principle of the waste heat utilization system comprises:
after hot secondary air required by combustion of the boiler 1 passes through the air preheater 2, the temperature of the hot secondary air at a hot secondary air outlet of the air preheater 2 is generally between 330 ℃ and 350 ℃. The thermodynamic part of the system can be divided into two complementary parts. The first part is a hot secondary air-water supply/condensed water heat exchanger 3, which extracts 330-350 ℃ bypass hot secondary air at a hot secondary air outlet of an air preheater 2 to heat water supply and condensed water, the water supply and condensed water side absorbs heat, the secondary air after heat release is mixed with the secondary air at an outlet of a blower 6 to enter the air preheater 2, the temperature of the mixed secondary air is about 50-80 ℃, the bypass hot secondary air overcomes the resistance of the air preheater 2 and the hot secondary air-water supply/condensed water heat exchanger 3, a bypass secondary fan 5 needs to be arranged at the outlet of the heat exchanger, and the pressure head is increased to be mixed with cold secondary air at the outlet of the blower 6 to return to the air preheater 2. In addition, an adjusting damper door 11 is arranged in the bypass hot secondary air duct, and the hot secondary air quantity can be adjusted to control the hot secondary air temperature at the outlet of the air preheater and the smoke exhaust temperature of the boiler.
The second part is a flue gas-air heat exchanger 4 which is arranged at the inlet of a dust remover 8 or the inlet of an absorption tower 10 and adopts water or other media as heat exchange intermediate media. The smoke side releases heat to the medium, and the medium releases heat to the air after absorbing heat. Since the air system is sucking air in the atmospheric environment, the temperature is equivalent to the ambient temperature, so that the flue gas entering the dust remover 8 or the absorption tower 10 can be reduced to a lower temperature. After being heated by the flue gas-air heat exchanger 4, the air is mixed with bypass secondary air and enters the air preheater 2 to exchange heat with flue gas. Because the hot secondary air partially bypasses and enters the hot secondary air-water supply/condensed water heat exchanger 3, the quantity of the hot secondary air entering the air preheater 2 is relatively increased, the heat absorption quantity of the air in the air preheater 2 is increased, and the air in the flue gas-air heat exchanger 4 absorbs heat, so that the problem of insufficient heat absorption in the air preheater can be solved, and the temperature of the hot air is ensured to be unchanged or even slightly increased (the temperature of the flue gas in the absorption tower is about 50 ℃, and the temperature of the flue gas at the inlet of the dust remover in the graph 2 is about 85-95 ℃).
It can be seen that the utility model discloses make full use of low temperature flue gas heats cold wind, and the hot overgrate air of the high temperature of replacement heats the condensate water or the feedwater of the higher temperature of steam turbine system, has reduced the feedwater of higher temperature and the steam of the higher quality that the condensate water needs, and flue gas waste heat utilization rate is higher. In addition, as the bypass secondary air heats the feed water and the condensed water, the secondary air has the characteristics of cleanness, no abrasion, no corrosion and the like, a soot blowing system is not required to be arranged, abrasion resistance and corrosion resistance do not need to be considered for the heat exchanger material, and the equipment cost is saved.
In addition, the proportion of the bypass hot secondary air, the final exhaust gas temperature and the heat exchange area required by the flue gas heat exchanger mainly depend on the following factors: (1) the temperature and flow of the feed water and the condensate at the extraction point; (2) the outlet temperature of the hot secondary air of the air preheater; (3) the procurement cost of hot overfire air-feedwater/condensate heat exchanger and flue gas-air heat exchanger systems; (4) the rising of the temperature of the feed water and the condensed water leads to the reduction of the extraction steam of the steam turbine, thereby saving the energy consumption of the steam turbine generator unit or generating more electric power; (5) the power consumption of a fan and a condensate pump is increased due to the increased resistance of the flue gas side and the condensate side of the flue gas heat exchanger system; (6) the power consumption of the bypass secondary fan is increased; (7) the change of the power consumption of the induced draft fan; (8) the profit brought by the water consumption saved by the desulfurization system; (9) suction temperature of air (ambient temperature); (10) the efficiency of the dust remover and the desulfurizing tower is improved to bring benefits; (11) other changes of the equipment configuration and the system configuration of the thermodynamic system and the smoke system of the power plant are caused by the arrangement of the scheme.
The embodiment is provided with the hot secondary air bypass, the cold air is heated by using the low-temperature flue gas, and the replaced high-temperature hot secondary air is used for heating the high-temperature water supply and the condensed water; and heating cold air by adopting low-temperature flue gas at the inlet of the dust remover or by adopting low-temperature flue gas at the inlet of the absorption tower. Namely, a first part of the hot secondary air-water supply/condensed water heat exchanger is arranged on a bypass secondary air channel of the air preheater to heat water supply and condensed water, and a second part of the flue gas-air heat exchanger system is arranged at the inlet of the dust remover or the inlet of the absorption tower to heat cold air through a medium.
After the system is adopted, the cold air is heated by using the low-temperature flue gas, the replaced high-temperature hot secondary air is used for heating the feed water and the condensed water with higher temperature of the steam turbine system, the utilization rate of the flue gas waste heat equivalent to that of an economizer system of bypass flue gas is achieved, the coal consumption of a thermal power generating unit can be greatly reduced, the efficiency of flue gas purification equipment, namely a dust remover and an absorption tower is improved, the power consumption of a draught fan is reduced, the water consumption of the absorption tower is reduced, and the discharge amount of dust and sulfur dioxide is reduced. In addition, compared with a system for efficiently replacing flue gas waste heat for utilizing flue gas by-pass, the system has the advantages of cleanness, no abrasion, no corrosion and the like, saves equipment cost, and has the characteristics of simple system, convenient operation and control and the like.
In addition, the system of the embodiment also comprises a turbine condensation water system and a turbine water supply system. The steam turbine condensation water system and the steam turbine water supply system can be the existing system in the power station boiler. For example, the system comprises a generator 16, a turbine high-pressure cylinder 17, a turbine intermediate-pressure cylinder 18, a turbine low-pressure cylinder 19, a condenser 20, a condensate pump 21, a multi-stage low-pressure heater 12, a deaerator 14, a feed water pump 15 and a multi-stage high-pressure heater 13.
Furthermore, the feed water heat exchanger can be connected with the high-pressure heater in series through full flow feed water, and can also be connected with a certain stage of high-pressure heater in parallel through partial flow feed water. The condensed water heat exchanger can be connected with the low-pressure heater in series by the full-flow condensed water, and can also be connected with a certain stage of low-pressure heater in parallel by the partial-flow condensed water. When the water supply and the condensed water are in full flow, the resistance of the flue gas heat exchanger and the water supply and condensed water pipelines at the inlet and the outlet of the flue gas heat exchanger is overcome by a water supply pump in a steam turbine water supply system and a condensed water pump in a condensed water system. When the partial flow of the water supply and the condensed water is calculated, the resistance of the heat exchanger and a pipeline is overcome by checking the water supply and the condensed water, and whether a pump needs to be added for the water supply and the condensed water to return the water supply and the condensed water to the thermodynamic system of the steam turbine or not is considered.
To sum up, the utility model discloses based on steam turbine thermodynamic cycle fundamental principle, the feedwater in steam turbine feedwater and the condensate water among the system and the hot overgrate air of condensate water cooling boiler bypass return the steam turbine feedwater and the condensate water system after being heated by hot overgrate air, because feedwater and condensate water temperature rise, arrange the extraction steam of partial heater, under the unchangeable condition of steam turbine admission volume, the extraction steam of being arranged crowded is at the turbine internal expansion acting, consequently, the generated energy of turbo generator has been increased under the unchangeable condition of unit coal consumption, the same principle, under the unchangeable condition of turbo generator generated energy, can practice thrift the coal consumption of unit. The utility model makes full use of the heat in the boiler flue gas through the heat secondary air-feed water/condensed water heat exchanger and the flue gas-air heat exchanger.
The utility model discloses a dust remover entry or absorption tower entry low temperature flue gas heat cold wind, and the cold wind rethread air preheater after the temperature risees heats to the hot-blast of burning needs, because the hot overgrate air bypass gets back to air preheater entry again and the mixed entering air preheater of forced draught blower export amount of wind, consequently overgrate air amount of wind increases in the air preheater. The hot overgrate air temperature is very high, and hot overgrate air-feedwater/condensate heat exchanger can heat the feedwater and the condensate of higher temperature, and the heating steam quality of squeezing is higher, and power generation ability is also stronger, consequently the utility model discloses can improve the utilization efficiency of flue gas waste heat by a wide margin.
The utility model discloses a hot overgrate air of hot overgrate air-feedwater/condensate heat exchanger heats feedwater and condensate, need not consider the heat exchanger abrasionproof anticorrosive problem, need not set up and blow the ash system, and equipment investment is low, and the system is simple, and convenient operation.
When the low-temperature flue gas in front of the dust remover is used for heating the cold secondary air, the efficiency of the dust remover can be improved, the power consumption of a draught fan is reduced, and the water consumption for desulfurization is reduced; when low-temperature flue gas in front of the desulfurization absorption tower is used for heating cold secondary air, the temperature of the flue gas entering the desulfurization absorption tower can be reduced, the evaporation capacity of water in the desulfurization absorption tower is reduced, the water consumption of a desulfurization system is reduced, and the desulfurization efficiency is improved. Therefore, the utility model provides high flue gas purification system's efficiency has reduced pollutant discharge.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention.
Claims (10)
1. A hot overgrate air and residual heat of flue gas utilize the system, wherein the said system includes air preheater, dust remover, absorption tower, hot overgrate air-feedwater/condensed water heat exchanger and flue gas-air heat exchanger;
a hot secondary air outlet of the air preheater is connected with a hot secondary air bypass, the hot secondary air bypass is connected with the hot secondary air-water supply/condensed water heat exchanger, and the hot secondary air is used for heating the water supply/condensed water;
the flue gas-air heat exchanger is arranged at the inlet of the dust remover, and the cold air is heated by using the low-temperature flue gas at the inlet of the dust remover; or,
the flue gas-air heat exchanger is arranged at the inlet of the absorption tower, and the cold air is heated by using the low-temperature flue gas at the inlet of the absorption tower.
2. The system for utilizing the hot secondary air and the waste heat of the flue gas as claimed in claim 1, wherein the air preheater is provided with a flue gas inlet, a primary cold air inlet, a secondary cold air inlet, a flue gas outlet and a hot secondary air outlet;
the flue gas inlet is connected with a flue gas outlet of a boiler furnace, the flue gas outlet is connected with an inlet of a flue gas-air heat exchanger, or the flue gas outlet is connected with an inlet of a dust remover;
the primary cold air inlet is connected with a primary fan;
the secondary cold air inlet is connected with an outlet of the hot secondary air-water supply/condensed water heat exchanger and/or an outlet of the flue gas-air heat exchanger;
the hot secondary air outlet is connected with the inlet of the hot secondary air-water supply/condensed water heat exchanger through a hot secondary air bypass.
3. The system for utilizing the waste heat of the hot secondary air and the flue gas as claimed in claim 2, wherein a bypass secondary fan is arranged on an outlet connecting pipeline of the hot secondary air-water supply/condensed water heat exchanger;
the flue gas-air heat exchanger is connected with the blower, and air is heated by the flue gas-air heat exchanger, then is discharged from an outlet of the flue gas-air heat exchanger, is mixed with bypass secondary air led out by the bypass secondary fan, and enters the air preheater through a secondary cold air inlet of the air preheater.
4. The system for utilizing the waste heat of the hot overgrate air and the flue gas as claimed in claim 1, wherein the heat exchange medium in the hot overgrate air-water supply/condensed water heat exchanger comprises water supply and/or condensed water, and the water supply and/or the condensed water are/is water supply and/or condensed water in a thermodynamic system of a steam turbine.
5. The system for utilizing the waste heat of the hot secondary air and the flue gas as claimed in claim 4, wherein the feed water is derived from a certain stage of high-pressure heater outlet or a summary of several stages of high-pressure heater outlets of a steam turbine feed water system;
and/or the condensed water is derived from a certain stage of low-pressure heater outlet or a plurality of stages of low-pressure heater outlets of the turbine condensed water system.
6. The system for utilizing the hot overgrate air and the waste heat of the flue gas as claimed in claim 4, wherein the flow rate of the feed water is full flow or partial flow, when the feed water is full flow, the hot overgrate air-feed water/condensed water heat exchanger is connected with the high-pressure heater in series, and when the feed water is partial flow, the hot overgrate air-feed water/condensed water heat exchanger is connected with the high-pressure heater in parallel;
and/or the condensed water is full flow or partial flow, when the condensed water is full flow, the hot secondary air-water supply/condensed water heat exchanger is connected with the low-pressure heater in series, and when the condensed water is partial flow, the hot secondary air-water supply/condensed water heat exchanger is connected with the low-pressure heater in parallel.
7. The system for utilizing the hot secondary air and the waste heat of the flue gas as claimed in claim 1, wherein an intermediate medium is arranged in the flue gas-air heat exchanger, and the low-temperature flue gas and the air exchange heat through the intermediate medium.
8. The system for utilizing the waste heat of the hot secondary air and the flue gas as claimed in claim 1, wherein the hot secondary air-water supply/condensed water heat exchanger is a heat pipe type heat exchanger or a surface type heat exchanger;
and/or the flue gas-air heat exchanger is a heat pipe type heat exchanger or a surface type heat exchanger.
9. The system for utilizing the waste heat of the hot secondary air and the flue gas as claimed in any one of claims 1 to 8, wherein a hot secondary air volume adjusting device and/or a hot secondary air temperature adjusting device is/are arranged on the hot secondary air bypass.
10. A thermal generator set, characterized in that, comprises the hot overgrate air and flue gas waste heat utilization system of any claim 1 ~ 9.
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| CN201920193697.7U CN209495348U (en) | 2019-02-12 | 2019-02-12 | Hot Secondary Air and smoke waste heat utilization system and thermal power generation unit |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109668165A (en) * | 2019-02-12 | 2019-04-23 | 中国电力工程顾问集团华东电力设计院有限公司 | Hot Secondary Air and smoke waste heat utilization system and thermal power generation unit |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109668165A (en) * | 2019-02-12 | 2019-04-23 | 中国电力工程顾问集团华东电力设计院有限公司 | Hot Secondary Air and smoke waste heat utilization system and thermal power generation unit |
| CN109668165B (en) * | 2019-02-12 | 2024-02-06 | 中国电力工程顾问集团华东电力设计院有限公司 | Hot secondary air and flue gas waste heat utilization system and thermal generator set |
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