CN115264565A - Low-pressure cylinder zero-output unit waste heat deep recovery optimized heating system - Google Patents
Low-pressure cylinder zero-output unit waste heat deep recovery optimized heating system Download PDFInfo
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- 239000002918 waste heat Substances 0.000 title claims abstract description 30
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- 238000010521 absorption reaction Methods 0.000 claims abstract description 39
- 238000005457 optimization Methods 0.000 claims abstract description 6
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- 239000008400 supply water Substances 0.000 abstract description 2
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- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 6
- 230000008901 benefit Effects 0.000 description 5
- 230000003287 optical effect Effects 0.000 description 5
- 239000000498 cooling water Substances 0.000 description 4
- 229910002092 carbon dioxide Inorganic materials 0.000 description 3
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D11/00—Central heating systems using heat accumulated in storage masses
- F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
- F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
- F24D11/0235—Central heating systems using heat accumulated in storage masses using heat pumps water heating system with recuperation of waste energy
- F24D11/0242—Central heating systems using heat accumulated in storage masses using heat pumps water heating system with recuperation of waste energy contained in exhausted air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D18/00—Small-scale combined heat and power [CHP] generation systems specially adapted for domestic heating, space heating or domestic hot-water supply
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D19/00—Details
- F24D19/10—Arrangement or mounting of control or safety devices
- F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
- F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
- F24D19/1039—Arrangement or mounting of control or safety devices for water heating systems for central heating the system uses a heat pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2101/00—Electric generators of small-scale CHP systems
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- 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
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Abstract
The invention discloses a low-pressure cylinder zero-output unit waste heat deep recovery optimized heating system, which divides a medium-pressure cylinder exhaust pipeline into three branches, and the three branches respectively enter an absorption heat pump, an exhaust heat exchanger and a peak heater. The return water of the heat supply network flowing out of the heat supply network firstly enters the absorption heat pump to be heated and then enters the steam exhaust heat exchanger, when the hot water flowing out of the steam exhaust heat exchanger can meet the requirement of water temperature, the hot water can directly enter the heat supply network to supply water, and when the temperature of the hot water flowing out of the steam exhaust heat exchanger can not meet the requirement of the water temperature, the hot water is heated by the peak heater and then enters the heat supply network. The invention aims at the currently exuberant low-pressure cylinder zero-output heat supply mode, develops a system capable of realizing high-efficiency and flexible recovery of low-grade waste heat in a matching way, realizes deep recovery and step energy supply of low-pressure exhaust waste heat through optimization and improvement of the thermal process of the low-pressure cylinder zero-output heat supply unit, obviously improves the whole heat supply economy of the unit, and simultaneously realizes improvement of the heat supply capacity of the unit.
Description
Technical Field
The invention belongs to the technical field of thermal power generating sets, and particularly relates to a low-pressure cylinder zero-output unit waste heat deep recovery optimized heating system.
Background
Since 2011, a plurality of power plants have real-time low-pressure optical axis heat supply transformation and high back pressure heat supply transformation in China, and the single-machine heat supply capacity and the heat supply economical efficiency are obviously improved by optimizing the heat supply operation mode of a unit. In 2017, a more flexible zero-output heating mode of the low-pressure cylinder is developed domestically on the basis of a low-pressure optical axis heating technology. At present, hundreds of units of 150 MW-600 MW grades are transformed into low-pressure cylinder zero-output heat supply (also called cylinder cutting heat supply), and the heat supply operation flexibility and the economy of the units are further remarkably improved.
And no matter the low-pressure cylinder runs in a zero-output heat supply mode or a low-pressure optical axis running unit, a large amount of cold source loss exists, and therefore the heat supply economical efficiency and the single-machine heat supply potential cannot be fully exerted. In addition, to this type of heat supply operation mode, it directly adopts a large amount of intermediate pressure cylinder steam exhaust heat supplies, and often pressure is on the high side and throttle by a wide margin, has the "high-quality low usefulness" problem of energy, and this is also showing and is influencing unit heat supply operation economic nature equally.
For a typical 300 MW-grade unit, the exhaust steam volume of a low-pressure cylinder during zero-output operation can reach more than 65t/h (the cooling steam flow of the low-pressure cylinder is 20t/h, and the exhaust steam flow of a water supply pump turbine can reach 45 t/h), the exhaust heat is completely discharged to the air through circulating cooling water and a water tower, and the energy loss is large. In addition, the discharge pressure in the domestic active power unit generally reaches 0.5-1.0 MPa, while the steam pressure at the inlet of the heat exchanger at the first station of the heat supply network generally only needs about 0.25MPa, so that large throttling decompression is required,
the loss is extremely large.
Therefore, in the heat supply period, although the running economy of the unit is greatly improved through cogeneration, a large amount of low-pressure exhaust steam waste heat is still not fully utilized, the heat supply steam flow is not reasonable, and a large energy-saving submerging space exists.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a low-pressure cylinder zero-output unit waste heat deep recovery optimized heating system to solve the problems that a large amount of low-pressure exhaust waste heat is not fully utilized and the flow of heating steam is unreasonable in the prior art.
In order to achieve the purpose, the invention adopts the following technical scheme to realize the purpose:
the optimized heat supply system for the deep recovery of the waste heat of the low-pressure cylinder zero-output unit comprises a medium-pressure cylinder steam exhaust pipeline, wherein the medium-pressure cylinder steam exhaust pipeline is divided into three branches, namely a first branch, a second branch and a third branch;
the first branch is connected to an absorption heat pump; the second branch is connected to a small power and heat turbine, and the exhaust steam output end of the small power and heat turbine is connected to a steam exhaust heat exchanger; the third branch is connected to a spike heater;
the cold side pipeline input end of the absorption heat pump is connected to the heat supply network water return pipeline, the cold side pipeline output end of the absorption heat pump is connected with the cold side pipeline input end of the steam exhaust heat exchanger, and the output end of the cold side pipeline of the steam exhaust heat exchanger is connected with the input end of the cold side pipeline of the peak heater, and the output end of the cold side pipeline of the peak heater is connected to a water supply pipeline of a heat supply network.
The invention is further improved in that:
preferably, the input end of the hot side pipeline of the absorption heat pump is connected with a condenser, and the output end of the hot side pipeline of the absorption heat pump is connected with a cooling tower.
Preferably, the input end of the hot side pipeline of the condenser is connected with a steam exhaust pipeline of the low-pressure cylinder.
Preferably, a cold side pipeline input end of the condenser is connected with the cooling tower, and a cold side pipeline output end of the condenser is connected with the absorption heat pump.
Preferably, the first branch is connected with a driving steam source pipeline of the absorption heat pump.
Preferably, the drive steam in the absorption heat pump does work and then is drained after doing work.
Preferably, the steam of the exhaust steam heat exchanger is drained after doing work.
Preferably, the steam of the peak heater is drained after doing work and becomes hydrophobic.
Preferably, an output shaft of the small power and heat turbine is connected with a generator.
Compared with the prior art, the invention has the following beneficial effects:
the invention discloses a low-pressure cylinder zero-output unit waste heat deep recovery optimized heating system, which divides a medium-pressure cylinder exhaust pipeline into three branches, and the three branches respectively enter an absorption heat pump, an exhaust heat exchanger and a peak heater. The return water of the heat supply network flowing out of the heat supply network firstly enters the absorption heat pump to be heated and then enters the steam exhaust heat exchanger, when the hot water flowing out of the steam exhaust heat exchanger can meet the requirement of water temperature, the hot water can directly enter the heat supply network to supply water, and when the temperature of the hot water flowing out of the steam exhaust heat exchanger can not meet the requirement of the water temperature, the hot water is heated by the peak heater and then enters the heat supply network. The invention aims at the currently exuberant low-pressure cylinder zero-output heat supply mode, develops a system capable of realizing high-efficiency and flexible recovery of low-grade waste heat in a matching way, realizes deep recovery and step energy supply of low-pressure exhaust waste heat through optimization and improvement of the thermal process of the low-pressure cylinder zero-output heat supply unit, obviously improves the overall heat supply economical efficiency of the unit, and simultaneously realizes the improvement of the heat supply capacity of the unit. The system is suitable for the heat supply unit with deep peak regulation demand in northern areas of China, can deeply recover the low-pressure exhaust waste heat of the low-pressure cylinder zero-output heat supply unit or the low-pressure optical axis heat supply unit, is used for heating the circulating water of a heat supply network, eliminates the loss of a cold source of the unit, and realizes the effective recovery of the exhaust waste heat of the low-pressure cylinder of the unit, thereby maximally excavating the heat supply potential and the heat supply economical efficiency of the unit.
Drawings
FIG. 1 is a heat supply flow chart of a conventional unit;
FIG. 2 is a heat supply flow chart of the unit of the present invention;
wherein: 1-a high pressure cylinder; 2-intermediate pressure cylinder; 3-low pressure cylinder; 4-intermediate pressure cylinder steam exhaust pipeline; 5-a first branch; 6-second branch; 7-third branch; 8-a condenser; 9-an absorption heat pump; 10-power-heating small steam turbine; 11-a steam exhaust heat exchanger; 12-spike heat exchangers; 13-a circulating water pump; 14-a cooling tower; 15-heat supply network return water pipeline; 16-heat supply network water supply pipeline.
Detailed Description
The invention is described in further detail below with reference to the accompanying drawings:
the invention relates to a step energy supply system suitable for a large-scale cogeneration power plant, which takes low-grade waste heat recovery and heat supply steam energy step utilization into overall consideration.
Referring to fig. 2, the system comprises a high-pressure cylinder 1, an intermediate-pressure cylinder 2, a low-pressure cylinder 3, an intermediate-pressure cylinder exhaust pipeline 4, a first branch 5, a second branch 6, a third branch 7, a condenser 8, an absorption heat pump 9, a small power and heat turbine 10, an exhaust heat exchanger 11 and a peak heat exchanger 12.
The steam exhaust pipeline 4 of the intermediate pressure cylinder 2 is divided into three branches, namely a first branch 5, a second branch 6 and a third branch 7, and the first branch 5 is communicated with the steam source pipeline of the absorption heat pump 9; the second branch 6 is connected with a small power and heat turbine 10, and a steam exhaust pipeline after the small power and heat turbine 10 applies work is communicated with a steam exhaust heat exchanger 11; the third branch 7 communicates with a spike heat exchanger 12.
The exhaust steam of the low-pressure cylinder 3 is communicated with the condenser 8 and serves as the hot side of the condenser 8, the exhaust steam pipeline of the low-pressure cylinder 3 is communicated with the steam inlet pipeline of the condenser 8, and the exhaust steam is cooled into condensed water in the condenser 8 and then is discharged; and a cold side pipeline inlet of the condenser 8 is communicated with a cooling tower 14 through a circulating water pump 13, the cooling tower 14 sends cooling water into the condenser 8, after the cooling water is heated by steam in the condenser 8, a cold side pipeline output end of the condenser 8 is connected with a hot side pipeline input end of the absorption heat pump 9, and a hot side pipeline output end of the absorption heat pump 9 is connected with an inlet of the cooling tower 14. The temperature of the water output from the cold-side pipeline of the condenser 8 is about 25 ℃, and the temperature of the cooling water output from the hot-side pipeline output end of the absorption heat pump 9 to the cooling tower 14 is about 20 ℃.
A driving steam source pipeline of the absorption heat pump 9 is communicated with the first branch 5, steam in the driving steam source does work and then becomes hydrophobic to be discharged, a hot side pipeline input end of the absorption heat pump 9 is connected with the condenser 8, a hot side pipeline output end of the absorption heat pump 9 is connected with the cooling tower 14, a cold side pipeline input end of the absorption heat pump 9 is connected with the heat supply network water return pipeline 15, and an output end of the cold side pipeline is connected with a cold side pipeline input end of the exhaust heat exchanger 11.
The hot side pipeline input end of the exhaust steam heat exchanger 11 is connected with the exhaust steam of the small power and heat turbine 9, the exhaust steam is cooled in the exhaust steam heat exchanger 11 to be drained and discharged, the cold side pipeline input end of the exhaust steam heat exchanger 11 is connected with the cold side pipeline output end of the absorption heat pump 9, and the cold side pipeline output end of the exhaust steam heat exchanger 11 is communicated with the cold side pipeline input end of the peak heat exchanger 12.
The input end of a hot side pipeline of the peak heater 12 is communicated with the third branch 7, steam is cooled in the peak heater 12 to become hydrophobic and discharged, the input end of a cold side pipeline of the peak heater 12 is connected with the output end of the cold side pipeline of the steam exhaust heat exchanger 11, and the output end of the cold side pipeline of the peak heater 12 is communicated with a heat supply network water supply pipeline 16.
The working process of the system of the invention is as follows:
(1) Step heating process for circulating water of heat supply network
The backwater of the circulating water of the heat supply network is heated in a cascade way by an absorption heat pump 9, an exhaust heat exchanger 11 of a small power and heat turbine 10 and a peak heat exchanger 12 at the first station of the heat supply network, wherein: the absorption heat pump 9 can heat the 50 ℃ heat supply network circulating water to about 65 ℃, the small power heat turbine 10 can further raise the temperature of the heat supply network circulating water to about 90 ℃ by exhausting steam, and the peak heat exchanger 12 can raise the temperature of the heat supply network circulating water to 110 ℃ or even higher according to actual needs.
In the initial and final stages of heat supply, the water supply temperature of the heat supply network generally reaches 90 ℃ to meet the heat supply requirement, and at the moment, the first two stages of heating are only needed to be put into use. When the cold season is entered, the peak heat exchanger 12 at the first station is put into the cold season according to actual requirements for heating, and the water supply temperature and the heat supply load are further improved.
(2) Heating steam step work flow
The low-pressure cylinder of the unit operates in zero-output heat supply mode, wherein the original flow of pressure steam exhaust directly enters the first-station heat exchanger to heat the circulating water of the heat supply network. In the optimization system, the steam extraction is divided into three paths, the first path of steam enters an absorption heat pump 9 and serves as a driving steam source of a heat pump set, the water outlet of a condenser 8 of a low-pressure cylinder zero-output unit is a low-level heat source of the heat pump set, and the extracted waste heat serves as a primary heat source to heat circulating water of a heat supply network; the second path of steam is driving steam of a small power-heating steam turbine generator unit, exhaust steam of the second path of steam enters a specially-arranged exhaust steam heat exchanger to serve as a secondary heat source for heating circulating water of a heat supply network, and electric power output by the power-heating steam turbine generator is connected into the unit to replace part of service power; the third path of steam is used as a steam source of the peak heater 12 at the initial station, is decompressed by the middle exhaust steam and is used as a three-level heat source to heat circulating water of a heat supply network, the flow of the part of steam is adjusted according to heat supply requirements, and the part of steam is generally flexibly put into operation under the condition of extremely cold weather according to actual heat supply requirements.
In order to realize the two core processes, the waste heat deep recovery optimized heating system needs to be combined with a low-pressure cylinder zero-output unit to carry out corresponding technical transformation, and an absorption heat pump unit, a power-heat steam turbine generator unit, a steam exhaust heat exchanger and other equipment, corresponding pipelines, valves and the like are additionally arranged.
Examples
The system provided by the invention is suitable for all low-pressure cylinder zero-output heat supply units, and can also be popularized and applied to low-pressure optical axis heat supply units. The analysis is carried out by taking a typical 300MW low-pressure cylinder zero-output heat supply unit as an example, if the optimization scheme provided by the invention is adopted for implementation and improvement, the low-grade waste heat recovery and heat supply process optimization can be realized, and the method has obvious economic benefits and environmental protection benefits:
1) In the first-stage heating process, the low-grade waste heat of the unit can be fully recovered, and the waste heat load can reach 48.3MW. The steam consumption driven by the heat pump in the process is about 95.5t/h, and the heat supply network circulating water temperature raising of 7500t/h can be realized at 13.4 ℃. The process can be selected according to 2 60MW absorption heat pump sets, the total reconstruction investment is about 3519 ten thousand yuan, the standard coal is saved by 20031 tons in corresponding years, and the coal income is increased by 2003 ten thousand yuan (converted according to the unit price of the standard coal of 1000 yuan/t).
TABLE 1 index of waste heat recovery economy
| Serial number | Item | Unit of | Parameter(s) |
| 1 | Capacity of unit | MW | 300.0 |
| 2 | Residual heat quantity of low-pressure cylinder of cylinder cutting unit is recovered | MW | 48.3 |
| 3 | Reduced newly-increased heat supply area | Wanping rice | 120.8 |
| 4 | Absorption heat pump COP | 1.7 | |
| 5 | Absorption heat pump heat capacity | MW | 117.3 |
| 6 | Driving a thermal load | MW | 69.0 |
| 7 | Driving steam flow | t/h | 95.5 |
| 8 | Long time of year heating | h | 2880.0 |
| 9 | Annual recovery cylinder cutting unit waste heat | GJ | 500774.4 |
| 10 | Reduced annual saving standard coal | Ton of | 20031.0 |
| 11 | Reduced coal-saving income | Wan Yuan | 2003.1 |
| 12 | Reduced annual carbon dioxide emission reduction | Ton of | 50077.4 |
| 13 | Investment for reforming absorption heat pump | Wan Yuan | 3519.0 |
| 14 | Reduced payback period | Year of year | 1.8 |
| 15 | Heat supply network circulation water flow | t/h | 7500.0 |
| 16 | First-stage temperature raising of heat supply network water | ℃ | 13.4 |
2) In the second-stage heating process, the energy gradient utilization of the heat supply and steam extraction of the unit can be realized. When the unit low pressure cylinder is operated with zero output for heat supply, the amount of discharged steam used for heat supply usually reaches 300-600t/h, 200-500t/h steam is subjected to direct throttling decompression except that 95.5t/h is consumed by a heat pump in a first-stage heating process,
the loss is huge. In the optimized heating system, the partial throttling can be replaced by a power-heating steam turbine and used for generating electricity, so that the purposes of saving electricity and improving efficiency are achieved. The process can recover the electric load to 20MW, and can be selected according to a 2 x 10MW back-pressure steam turbine generator unit, wherein the steam pressure of an inlet of a small steam turbine is 0.7MPa, the steam pressure of an outlet is 0.2MPa, the rated steam flow of a single machine is 150t/h, the generator is an asynchronous generator with a relatively simple structure, the output electric load is connected into a 6000V plant power system of the machine, and two small machines are respectively provided with corresponding dead steam heat exchangers so as to realize independent operation. In the process, annual service power is saved by 57863MWh, 9895 tons of standard coal can be saved every year on the premise of keeping the heat supply load unchanged, and 990 ten thousand yuan of coal saving benefit is directly realized by reduction in annual increase. The steam consumption driven by the heat pump in the process is about 300t/h, and the circulating water temperature of the heat supply network can be increased by 23.1 ℃ at 7500 t/h.
TABLE 2 economic index for cascade utilization of heat supply steam energy
| Serial number | Item | Unit of | Parameter(s) |
| 1 | Steam inlet flow of small power heating machine | t/h | 300.0 |
| 2 | Inlet pressure of small machine | MPa | 0.8 |
| 3 | Inlet temperature of small machine | ℃ | 290.0 |
| 4 | Enthalpy of admission of small machine | kJ/kg | 3035.8 |
| 5 | Small machine steam inlet entropy | kJ/(kg*℃) | 7.2 |
| 6 | Exhaust pressure of small machine | MPa | 0.2 |
| 7 | Small mechanism ideal exhaust enthalpy | kJ/kg | 2734.4 |
| 8 | Small mechanism enthalpy drop | kJ/kg | 301.4 |
| 9 | Small machine efficiency | ％ | 80.0 |
| 10 | Actual enthalpy drop of small machine | kJ/kg | 241.1 |
| 11 | Exhaust enthalpy of small machine | kJ/kg | 2794.7 |
| 12 | Exhaust temperature of small machine | ℃ | 162.5 |
| 13 | Small electromechanical power | MW | 20.1 |
| 14 | Long time of year heating | h | 2880.0 |
| 15 | Annual plant power saving | MWh | 57863.2 |
| 16 | Annual saving standard coal | t | 9894.6 |
| 17 | Reduced coal-saving income | Wan Yuan | 989.5 |
| 18 | Reduced annual carbon dioxide emission reduction | Ton of | 24736.5 |
| 19 | Exhaust saturated water temperature | ℃ | 120.2 |
| 20 | Exhaust steam drainage enthalpy | kJ/kg | 377.1 |
| 21 | Exhaust steam exhaust heat load | MW | 201.5 |
| 22 | Heat supply network circulation water flow | t/h | 7500.0 |
| 23 | Two-stage temperature raising for heat supply network water | ℃ | 23.1 |
3) The scheme can save 29926 tons of standard coal each year and reduce 74814 tons of carbon dioxide each year;
4) The improvement of the scheme has about 5819 ten thousand yuan, the direct coal saving benefit can reach 2992 ten thousand yuan after the annual increase, all investment can be recovered in 2 years, and the economic benefit is remarkable.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (9)
1. The optimized heating system for deep recovery of waste heat of the low-pressure cylinder zero-output unit is characterized by comprising a medium-pressure cylinder steam exhaust pipeline (4), wherein the medium-pressure cylinder steam exhaust pipeline (4) is divided into three branches, namely a first branch (5), a second branch (6) and a third branch (7);
the first branch (5) is connected to an absorption heat pump (9); the second branch (6) is connected to a small power and heat turbine (10), and the exhaust steam output end of the small power and heat turbine (10) is connected to an exhaust steam heat exchanger (11); the third branch (7) is connected to a spike heater (12);
the cold side pipeline input end of the absorption heat pump (9) is connected to a heat supply network water return pipeline (15), the cold side pipeline output end of the absorption heat pump (9) is connected with the cold side pipeline input end of the steam exhaust heat exchanger (11), the cold side pipeline output end of the steam exhaust heat exchanger (11) is connected with the cold side pipeline input end of the peak heater (12), and the cold side pipeline output end of the peak heater (12) is connected to a heat supply network water supply pipeline (16).
2. The system for deeply recycling and optimizing the waste heat of the low-pressure cylinder zero-output unit according to claim 1, wherein an input end of a hot-side pipeline of the absorption heat pump (9) is connected with a condenser (8), and an output end of the hot-side pipeline of the absorption heat pump (9) is connected with a cooling tower (14).
3. The system for deeply recycling and optimizing the waste heat of the low-pressure cylinder zero-output unit according to claim 2, characterized in that an input end of a hot side pipeline of the condenser (8) is connected with a steam exhaust pipeline of the low-pressure cylinder (3).
4. The system for deeply recycling and optimizing the heat supply of the low-pressure cylinder zero-output unit waste heat according to claim 2, characterized in that a cold side pipeline input end of the condenser (8) is connected with the cooling tower (14), and a cold side pipeline output end of the condenser (8) is connected with the absorption heat pump (9).
5. The system for deep recovery and optimization of waste heat supply of low-pressure cylinder zero-output unit according to claim 1, characterized in that the first branch (5) is connected with a driving steam source pipeline of the absorption heat pump (9).
6. The system of claim 1, wherein the steam driven work in the absorption heat pump (9) is drained after the steam is driven to do work.
7. The system for deeply recycling and optimizing the heat supply of the waste heat of the low-pressure cylinder zero-output unit as claimed in claim 1, wherein the steam of the exhaust steam heat exchanger (11) is drained after acting.
8. The system of claim 1, wherein steam from the spike heater (12) is drained as hydrophobic after performing work.
9. The low-pressure cylinder zero-output unit waste heat deep recovery optimized heating system of any one of claims 1 to 8, characterized in that an output shaft of the small power and heat turbine (10) is connected with a generator.
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102220888A (en) * | 2011-05-11 | 2011-10-19 | 北京创时能源有限公司 | Method and system for recovering circulating water residual heat of thermal power plants |
| KR20130086397A (en) * | 2012-01-25 | 2013-08-02 | (주) 씨테크놀로지시스템 | The power efficiency improvement by using absorption heat pump in power plant system |
| CN106091074A (en) * | 2016-06-16 | 2016-11-09 | 北京龙威发电技术有限公司 | A kind of absorption heat pump heating extraction for heat supply system |
| CN205957280U (en) * | 2016-06-16 | 2017-02-15 | 北京龙威发电技术有限公司 | Absorption heat pump heating steam extracting and heat supplying system |
| CN106988810A (en) * | 2017-04-24 | 2017-07-28 | 中国华能集团清洁能源技术研究院有限公司 | The multi-stage heating system and method for a kind of waste heat overbottom pressure cascade utilization |
| CN206890633U (en) * | 2017-05-26 | 2018-01-16 | 华北电力大学 | A kind of recovery exhausted spare heat system in parallel based on absorption heat pump and high back pressure |
| CN208504512U (en) * | 2018-06-15 | 2019-02-15 | 华北电力大学 | A kind of absorption type heat pump heat distribution system based on cascaded utilization of energy |
| CN113375208A (en) * | 2021-06-28 | 2021-09-10 | 大唐环境产业集团股份有限公司 | Heat supply method, system and device of coal-fired unit coupling absorption heat pump |
| CN215333021U (en) * | 2021-05-10 | 2021-12-28 | 河北冀研能源科学技术研究院有限公司 | Residual pressure and waste heat utilization system for heat supply air cooling unit changed from straight condensing |
| CN114110714A (en) * | 2021-11-29 | 2022-03-01 | 西安西热节能技术有限公司 | Low-pressure cylinder low-flow working condition waste heat deep recovery heat supply system and application method thereof |
-
2022
- 2022-07-25 CN CN202210878741.4A patent/CN115264565A/en active Pending
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102220888A (en) * | 2011-05-11 | 2011-10-19 | 北京创时能源有限公司 | Method and system for recovering circulating water residual heat of thermal power plants |
| KR20130086397A (en) * | 2012-01-25 | 2013-08-02 | (주) 씨테크놀로지시스템 | The power efficiency improvement by using absorption heat pump in power plant system |
| CN106091074A (en) * | 2016-06-16 | 2016-11-09 | 北京龙威发电技术有限公司 | A kind of absorption heat pump heating extraction for heat supply system |
| CN205957280U (en) * | 2016-06-16 | 2017-02-15 | 北京龙威发电技术有限公司 | Absorption heat pump heating steam extracting and heat supplying system |
| CN106988810A (en) * | 2017-04-24 | 2017-07-28 | 中国华能集团清洁能源技术研究院有限公司 | The multi-stage heating system and method for a kind of waste heat overbottom pressure cascade utilization |
| CN206890633U (en) * | 2017-05-26 | 2018-01-16 | 华北电力大学 | A kind of recovery exhausted spare heat system in parallel based on absorption heat pump and high back pressure |
| CN208504512U (en) * | 2018-06-15 | 2019-02-15 | 华北电力大学 | A kind of absorption type heat pump heat distribution system based on cascaded utilization of energy |
| CN215333021U (en) * | 2021-05-10 | 2021-12-28 | 河北冀研能源科学技术研究院有限公司 | Residual pressure and waste heat utilization system for heat supply air cooling unit changed from straight condensing |
| CN113375208A (en) * | 2021-06-28 | 2021-09-10 | 大唐环境产业集团股份有限公司 | Heat supply method, system and device of coal-fired unit coupling absorption heat pump |
| CN114110714A (en) * | 2021-11-29 | 2022-03-01 | 西安西热节能技术有限公司 | Low-pressure cylinder low-flow working condition waste heat deep recovery heat supply system and application method thereof |
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