CN110926049B - Cogeneration low-temperature heating process and system - Google Patents

Cogeneration low-temperature heating process and system Download PDF

Info

Publication number
CN110926049B
CN110926049B CN201911232468.2A CN201911232468A CN110926049B CN 110926049 B CN110926049 B CN 110926049B CN 201911232468 A CN201911232468 A CN 201911232468A CN 110926049 B CN110926049 B CN 110926049B
Authority
CN
China
Prior art keywords
low
heat
temperature
supply network
heat supply
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201911232468.2A
Other languages
Chinese (zh)
Other versions
CN110926049A (en
Inventor
胡波
张瑾
田玉宝
曹龙
种蕊
曹锐鑫
艾腾飞
尚敏青
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shaanxi Blower Group Co ltd
Original Assignee
Shaanxi Blower Group Co ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shaanxi Blower Group Co ltd filed Critical Shaanxi Blower Group Co ltd
Priority to CN201911232468.2A priority Critical patent/CN110926049B/en
Publication of CN110926049A publication Critical patent/CN110926049A/en
Application granted granted Critical
Publication of CN110926049B publication Critical patent/CN110926049B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/006—Auxiliaries or details not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • 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
    • F24D15/00—Other domestic- or space-heating systems
    • F24D15/02—Other domestic- or space-heating systems consisting of self-contained heating units, e.g. storage heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • Y02E20/14—Combined heat and power generation [CHP]

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

The application provides a cogeneration low-temperature heating process and a system, which realize heating of low-temperature backwater of a heat supply network through exhaust heat of a thermal power plant, wherein the exhaust heat of the thermal power plant and the low-temperature backwater of the heat supply network exchange heat, and the low-temperature backwater of the heat supply network after heat exchange is subjected to pressure reduction and gas-liquid separation in sequence to generate low-temperature liquid water and low-pressure steam; the low-temperature liquid water is pressurized and then returns to the thermal power plant through the heat supply network to circularly absorb heat, the low-pressure steam is pressurized and then is subjected to heat exchange with low-temperature backwater of the heat supply network to be converted into supercooled water, and part of supercooled water is pressurized and then is subjected to gas-liquid separation and circulation to supplement low-pressure steam. The application provides an economically feasible scheme capable of replacing the current high-cost cogeneration heating process.

Description

Cogeneration low-temperature heating process and system
Technical Field
The application relates to comprehensive utilization of waste heat, in particular to a cogeneration low-temperature heating process and system.
Background
In recent years, geothermal heating, biomass heating, solar heating, natural gas heating, electric heating, industrial waste heat heating, clean coal-fired central heating, coal-to-gas heating and the like are sequentially promoted according to local conditions in northern areas. In a plurality of heating technologies, the cogeneration has obvious advantages over other heating modes in terms of energy utilization rate and economy, and the large-scale thermal power plant has complete environmental protection facilities, thereby being a heating mode which is popularized preferentially. From the energy conversion perspective, the cogeneration considers the urban heating requirement, the water supply temperature is usually about 90 ℃ and even higher (such as long-distance pipeline heating), the turbine utilizes high-temperature steam expansion to do work, the generated power is used for generating electricity, under ideal working conditions, the exhaust pressure of the condensing turbine is about 5KPa, the corresponding saturated temperature is 32.88 ℃, and after the steam corresponding to the temperature is cooled by circulating water in the condenser, the heat is discharged to the atmosphere through the cooling tower. The heat and power cogeneration utilizes a back pressure unit, and the saturation temperature corresponding to the exhaust pressure of a back pressure turbine is higher than 90 ℃ to heat the circulating water of the heat supply network, so that the heat originally discharged into the atmosphere is used for heating, and the heat efficiency of the system is improved.
At present, a gas absorption heat pump is used for heating in the market, the cop is about 1.8, but the investment cost of the gas absorption heat pump is high. The market needs a low-cost heating mode for reducing the return water temperature of a heat supply network and improving the utilization efficiency of fuel gas.
Disclosure of Invention
Aiming at the defects existing in the prior art, the application aims at: the utility model provides a cogeneration low temperature heating technology and system, mainly solves the problem that current cogeneration heating system investment is high, with high costs.
In order to solve the technical problems, the application adopts the following technical scheme:
the application provides a cogeneration low-temperature heating process, which realizes heating of low-temperature backwater of a heat supply network through exhaust heat of a thermal power plant, wherein the exhaust heat of the thermal power plant and the low-temperature backwater of the heat supply network are subjected to heat exchange, and the low-temperature backwater of the heat supply network after heat exchange is subjected to pressure reduction and gas-liquid separation in sequence to generate low-temperature liquid water and low-pressure steam; the low-temperature liquid water is pressurized and then returns to the thermal power plant through the heat supply network to circularly absorb heat, the low-pressure steam is pressurized and then is subjected to heat exchange with low-temperature backwater of the heat supply network to be converted into supercooled water, and part of supercooled water is pressurized and then is subjected to gas-liquid separation and circulation to supplement low-pressure steam.
Preferably, the thermal power plant comprises a multistage steam power system, the multistage steam power system realizes multistage heating of low-temperature backwater of the heat supply network through one of series combination, parallel combination and series-parallel combination, and the multistage comprises at least one stage.
Meanwhile, the application also provides a cogeneration low-temperature heating system, which realizes low-temperature backwater heating of the heat supply network by exhaust heat of the thermal power plant and comprises a low-temperature backwater heat exchange unit I of the heat supply network and a low-temperature backwater heat exchange unit II of the secondary heat supply network;
the heat supply network low-temperature backwater heat exchange unit I is used for carrying out heat exchange on exhaust heat of the thermal power plant and the heat supply network low-temperature backwater, the heat supply network low-temperature backwater after heat exchange sequentially passes through the pressure reducing device and the gas-liquid separating device to generate low-temperature liquid water and low-pressure steam, and the low-temperature liquid water is returned to the thermal power plant through the heat supply network for cyclic heat absorption after being pressurized;
the second-level heat supply network low-temperature backwater heat exchange unit II is used for performing heat exchange between low-pressure steam generated by the heat supply network low-temperature backwater heat exchange unit I and heat supply network low-temperature backwater through the ejector to convert the low-pressure steam into supercooled water, and part of supercooled water is pressurized and then circularly enters the gas-liquid separation device to supplement the low-pressure steam.
Still further, the remaining portion of the supercooled water is passed through the heating means to generate the working steam required for the ejector.
Optionally, the pressure reducing device comprises one of an expansion valve, a pressure reducing valve, an expander and a regulating valve.
Optionally, the gas-liquid separation device comprises one of an expander, an expansion tank or a flash tank.
Optionally, the heating device comprises one of a gas boiler, an electric heating device or a gas heating device.
Compared with the prior art, the application has the following technical effects:
the application provides an economically feasible scheme capable of replacing the existing high-cost cogeneration heating process, and utilizes the mode of realizing temperature reduction by water steam-water separation under low pressure and reducing backwater temperature through heat exchange. The low-cost gas boiler, the expander and the ejector are adopted to replace a complex and expensive system of an absorption scheme and a compression scheme, so that the equipment investment cost can be effectively reduced, and the comprehensive cost is better than that of the absorption scheme and the compression scheme.
Drawings
FIG. 1 is a schematic diagram of the system principle of the present application.
Fig. 2 is a schematic and simplified illustration of the system principle of the application without reference numerals.
The meaning of each reference numeral in the figures is:
1-steam turbine, 2-condenser, 3-circulating pump, 4-heat user heat exchanger, 5-choke I, 6-expansion vessel, 7-water pump I, 8-choke II, 9-gas boiler, 10-water pump II, 11-governing valve, 12-heat exchanger, 13-sprayer.
The details of the application are explained in further detail below with reference to the accompanying drawings.
Detailed Description
The following specific embodiments of the present application are provided, and it should be noted that the present application is not limited to the following specific embodiments, and all equivalent changes made on the basis of the technical scheme of the present application fall within the protection scope of the present application.
The cogeneration of the application refers to a process for simultaneously producing electricity and heat energy, and saves fuel compared with a mode of respectively producing electricity and heat energy.
Meanwhile, the heat supply network, namely a heat supply pipe network, is also called a heat supply pipeline, and starts from a boiler room, a direct-fired machine room, a heat supply center and the like, and leads from a heat source to a heat supply inlet of a building. The plurality of heating pipes form a pipe network or a heat supply network.
Example 1:
according to the technical scheme, as shown in fig. 1-2, the embodiment provides a cogeneration low-temperature heating system, which realizes low-temperature backwater heating of a heat supply network through exhaust heat of a thermal power plant and comprises a low-temperature backwater heat exchange unit I of the heat supply network and a low-temperature backwater heat exchange unit II of a secondary heat supply network;
the heat supply network low-temperature backwater heat exchange unit I is used for carrying out heat exchange on exhaust heat of the thermal power plant and the heat supply network low-temperature backwater, the heat supply network low-temperature backwater after heat exchange sequentially passes through the pressure reducing device and the gas-liquid separating device to generate low-temperature liquid water and low-pressure steam, and the low-temperature liquid water is returned to the thermal power plant through the heat supply network for cyclic heat absorption after being pressurized;
the second-level heat supply network low-temperature backwater heat exchange unit II is used for performing heat exchange between low-pressure steam generated by the heat supply network low-temperature backwater heat exchange unit I and heat supply network low-temperature backwater through the ejector to convert the low-pressure steam into supercooled water, and part of supercooled water is pressurized and then circularly enters the gas-liquid separation device to supplement the low-pressure steam.
Still further, the remaining portion of the supercooled water is passed through the heating means to generate the working steam required for the ejector.
Optionally, the pressure reducing device comprises one of an expansion valve, a pressure reducing valve, an expander and a regulating valve.
Optionally, the gas-liquid separation device comprises one of an expander, an expansion tank or a flash tank.
Optionally, the heating device comprises one of a gas boiler, an electric heating device or a gas heating device.
The working process of the system of the application is as follows:
the exhaust gas of the steam turbine 1 of the thermal power plant is cooled in the condenser 2, the exhaust gas of the steam turbine returns to the boiler again after being changed into condensed water, the condensed water enters the next round of power generation circulation, the heat of the exhaust gas of the steam turbine is transferred to the circulating water of the heat supply network, the circulating hot water is transferred to the heat exchange station of the terminal heat user through the heat supply network, and the equipment and the pipeline in the wire selection frame in the figure 1 are all in the heat exchange station of the terminal heat user. The hot, low temperature water exchanges heat with the consumer secondary network at the hot consumer heat exchanger 4. The backwater after heat exchange is depressurized to about 5KPa through a throttle valve 5 and enters a flash tank 6. The backwater is separated into gas-liquid two phases in the flash vessel 6. The 5KPa low-temperature liquid water is pressurized by a water pump 7, the water pressure is increased to a heat supply network set value, the heat supply network backwater is entered, and backwater returns to the turbine condenser 2 through the circulating pump 3 of the thermal power plant to absorb heat and enter the next cycle. The 5KPa low pressure steam enters the ejector 13 as injection steam. The ejector 13 drives steam from the gas boiler, jet steam from the flash tank 6, the temperature of the mixed steam is set to be higher than the water supply temperature of the heat supply network, the mixed steam heats the return water of the heat supply network in the heat exchanger 12, and the mixed steam is condensed into supercooled water. Two paths of condensed water discharged by the heat exchanger 12 are pressurized by a throttle valve 8 and enter the flash tank 6 for supplementing low-pressure steam discharged by the flash tank 6; one path is used as working steam required by the boiler water supply ejector 13.
The heat exchanger 4 for the heat user can also directly supply heat to the user by adopting hot water of a primary network, release heat and have no secondary network.
The throttle valves 5 and 8 have throttle and pressure reducing functions, and the functions can be realized by pressure reducing devices like expansion valves, pressure reducing valves, expanders, regulating valves, self-operated pressure regulating valves and the like, and the protection scope of the application also belongs to the protection scope of the application.
The expander 6 is a gas-liquid two-phase separation device, and containers like an expander and an expansion tank can realize the function, and also belong to the protection scope of the application.
The gas boiler 9 directly generates steam as an ejector driving heat source, or a hot water boiler can be adopted, and the generated high-pressure hot water passes through the expander to generate steam as an ejector driving heat source, which also belongs to the protection scope of the patent.
The heating device realizes the heating function in other heating modes like electric heating and various gas heating, and also belongs to the protection scope of the application.
As shown in FIG. 2, when a plurality of steam turbines on the thermal power plant side are connected in series and parallel, the return water of the heat supply network is heated step by step, so that the maximum heat energy utilization efficiency is realized, and the application also belongs to the protection scope.
The heat power plant side multiple steam turbines are connected in parallel or in series-parallel combination to realize the return water heating of the heat supply network, and the application also belongs to the protection scope.
Effect evaluation:
as shown in the following table, the solution of this example is compared with the absorption solution and the compression solution, and the economy of the different solutions is calculated by taking low-temperature backwater for recovering 1MW of heat as an example. The injection scheme utilizes the steam-water separation of water under low pressure to realize temperature reduction, and the non-absorption scheme and the compression scheme reduce backwater temperature through the mode of preparing working media with lower temperature and through heat exchange. Because the injection scheme adopts a low-cost gas boiler, an expander and an ejector to replace a complex and expensive system of an absorption scheme and a compression scheme, the equipment investment cost can be effectively reduced, and the comprehensive cost is better than that of the absorption scheme and the compression scheme.
The foregoing is only a preferred embodiment of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art, who is within the scope of the present application, should be covered by the protection scope of the present application by equally replacing or changing the technical scheme and the inventive concept thereof.

Claims (5)

1. The system realizes low-temperature backwater heating of a heat supply network through exhaust heat of a thermal power plant according to the low-temperature heating process of the heat and power cogeneration, and is characterized by comprising a low-temperature backwater heat exchange unit I of the heat supply network and a low-temperature backwater heat exchange unit II of a secondary heat supply network;
the thermal power plant comprises a multi-stage steam power system, the multi-stage steam power system realizes multi-stage heating of low-temperature backwater of a heat supply network through one of a series combination, a parallel combination and a series-parallel combination, and the multi-stage comprises at least one stage;
the heat supply network low-temperature backwater heat exchange unit I is used for carrying out heat exchange on exhaust heat of the thermal power plant and the heat supply network low-temperature backwater, the heat supply network low-temperature backwater after heat exchange sequentially passes through the pressure reducing device and the gas-liquid separating device to generate low-temperature liquid water and low-pressure steam, and the low-temperature liquid water is returned to the thermal power plant through the heat supply network for cyclic heat absorption after being pressurized;
the second-level heat supply network low-temperature backwater heat exchange unit II is used for performing heat exchange between low-pressure steam generated by the heat supply network low-temperature backwater heat exchange unit I and heat supply network low-temperature backwater through the ejector to convert the low-pressure steam into supercooled water, and part of supercooled water is pressurized and then circularly enters the gas-liquid separation device to supplement the low-pressure steam.
2. A cogeneration low temperature heating system according to claim 1, wherein the remaining portion of the superheated water is passed through a heating device to produce the working steam required by the ejector.
3. A cogeneration low temperature heating system according to claim 1 or 2, wherein said pressure reducing means comprises one of an expansion valve, a pressure reducing valve, an expander, a regulator valve.
4. A cogeneration low temperature heating system according to claim 1 or 2, wherein said gas-liquid separation device comprises one of an expander, an expansion tank or a flash tank.
5. The cogeneration low temperature heating system of claim 2, wherein the heating device comprises one of a gas boiler, an electric heating device, or a gas heating device.
CN201911232468.2A 2019-12-05 2019-12-05 Cogeneration low-temperature heating process and system Active CN110926049B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201911232468.2A CN110926049B (en) 2019-12-05 2019-12-05 Cogeneration low-temperature heating process and system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201911232468.2A CN110926049B (en) 2019-12-05 2019-12-05 Cogeneration low-temperature heating process and system

Publications (2)

Publication Number Publication Date
CN110926049A CN110926049A (en) 2020-03-27
CN110926049B true CN110926049B (en) 2023-11-21

Family

ID=69856863

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201911232468.2A Active CN110926049B (en) 2019-12-05 2019-12-05 Cogeneration low-temperature heating process and system

Country Status (1)

Country Link
CN (1) CN110926049B (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112728619A (en) * 2020-12-29 2021-04-30 吉林同鑫热力集团股份有限公司 Energy-saving heating system for improving heat supply backwater utilization rate
CN114279109A (en) * 2021-12-29 2022-04-05 北京华源泰盟节能设备有限公司 High-efficient gas waste heat utilization system

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000221297A (en) * 1999-01-28 2000-08-11 Toshiba Corp Process and system for power generation by utilizing spent fuel
JP2001234709A (en) * 2000-02-25 2001-08-31 Toshiba Corp Mixed medium power generating system
WO2006078139A1 (en) * 2005-01-20 2006-07-27 Korea Energy Equipment Research Institute Co., Ltd Combined local heating system and central heating system
CN202869080U (en) * 2012-09-17 2013-04-10 中能东讯新能源科技(大连)有限公司 Device for recovering low-pressure steam and cooling water waste heat of waste heat power generation system
CN202869079U (en) * 2012-08-25 2013-04-10 中能东讯新能源科技(大连)有限公司 Condensate water heating device utilizing power plant circulating cooling water waste heat recovered by jet-type heat pump
CN103629860A (en) * 2013-12-04 2014-03-12 重庆大学 Transcritical CO2 cooling heat and power combined circulation system
CN203489341U (en) * 2013-09-15 2014-03-19 张茂勇 Superlarge temperature difference heat supply network waste heat heating system combined with low-vacuum injection type heat pump
CN103787434A (en) * 2013-12-19 2014-05-14 潘庆光 Power-water-salt coproduction process for condensing steam turbine generator unit
CN104315583A (en) * 2014-09-23 2015-01-28 大连葆光节能空调设备厂 Energy-saving heat supply system for reducing heat supply return water temperature and recovering city waste heat
CN204227750U (en) * 2014-11-12 2015-03-25 广东冠华机电工程有限公司 Cooling water of thermoelectric plant heat recovery steam drives compression type heat heat pump heating system
CN207813667U (en) * 2017-12-19 2018-09-04 华电电力科学研究院 Low pressure cylinder cooling system based on different steam ports
CN108679682A (en) * 2018-03-13 2018-10-19 东南大学 It recycles thermal power plant dry method and traps CO2Process waste heat and the system for being used for heat supply
CN211372815U (en) * 2019-12-05 2020-08-28 陕西鼓风机（集团）有限公司 Cogeneration low temperature heating system

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000221297A (en) * 1999-01-28 2000-08-11 Toshiba Corp Process and system for power generation by utilizing spent fuel
JP2001234709A (en) * 2000-02-25 2001-08-31 Toshiba Corp Mixed medium power generating system
WO2006078139A1 (en) * 2005-01-20 2006-07-27 Korea Energy Equipment Research Institute Co., Ltd Combined local heating system and central heating system
CN202869079U (en) * 2012-08-25 2013-04-10 中能东讯新能源科技(大连)有限公司 Condensate water heating device utilizing power plant circulating cooling water waste heat recovered by jet-type heat pump
CN202869080U (en) * 2012-09-17 2013-04-10 中能东讯新能源科技(大连)有限公司 Device for recovering low-pressure steam and cooling water waste heat of waste heat power generation system
CN203489341U (en) * 2013-09-15 2014-03-19 张茂勇 Superlarge temperature difference heat supply network waste heat heating system combined with low-vacuum injection type heat pump
CN103629860A (en) * 2013-12-04 2014-03-12 重庆大学 Transcritical CO2 cooling heat and power combined circulation system
CN103787434A (en) * 2013-12-19 2014-05-14 潘庆光 Power-water-salt coproduction process for condensing steam turbine generator unit
CN104315583A (en) * 2014-09-23 2015-01-28 大连葆光节能空调设备厂 Energy-saving heat supply system for reducing heat supply return water temperature and recovering city waste heat
CN204227750U (en) * 2014-11-12 2015-03-25 广东冠华机电工程有限公司 Cooling water of thermoelectric plant heat recovery steam drives compression type heat heat pump heating system
CN207813667U (en) * 2017-12-19 2018-09-04 华电电力科学研究院 Low pressure cylinder cooling system based on different steam ports
CN108679682A (en) * 2018-03-13 2018-10-19 东南大学 It recycles thermal power plant dry method and traps CO2Process waste heat and the system for being used for heat supply
CN211372815U (en) * 2019-12-05 2020-08-28 陕西鼓风机（集团）有限公司 Cogeneration low temperature heating system

Also Published As

Publication number Publication date
CN110926049A (en) 2020-03-27

Similar Documents

Publication Publication Date Title
CN108316980B (en) Fused salt heat accumulation and release peak shaving system of thermal power generating unit
CN110345541B (en) Thermoelectric cooperative heat supply system and method for gas thermal power plant
CN103850901A (en) Solar cogeneration system and method based on double-working medium thermodynamic cycle
CN109869205B (en) Heat storage, power generation and heat supply system for cogeneration unit
CN210345602U (en) Large-temperature-difference central heating system utilizing electric compression heat pump
CN102454440A (en) Solar energy and thermal power station complementary power generation system with plate and groove combined
CN215170241U (en) Energy storage peak regulation coupling system of thermal power plant
CN110926049B (en) Cogeneration low-temperature heating process and system
CN211903494U (en) Liquefied air energy storage power generation system coupled with steam-water system of coal-fired power generating unit
CN211372815U (en) Cogeneration low temperature heating system
CN210118178U (en) Combined power generation system based on waste incineration waste heat and photo-thermal
CN113237134B (en) Geothermal energy central heating system based on electric heat pump unit
CN215170240U (en) Heat-storage peak regulation system of thermal power plant
CN214741510U (en) Waste heat auxiliary heating condensate system for supercritical carbon dioxide circulation cold end
CN108843406B (en) Flue gas reheating type disc type photo-thermal and gas-steam combined cycle power generation system
CN114439560A (en) Thermoelectric compressed air energy storage system and method adopting thermoelectric unit for extracting steam and storing heat
CN211777845U (en) Geothermal photo-thermal combined type continuous power generation system
CN201827034U (en) Plate-trough combined solar and thermal power station complementary power generating system
CN205243745U (en) Natural gas distributed energy system coupled with solar energy
CN201246193Y (en) Thermal storage power generating apparatus utilizing solar energy and air heat energy extraction technology
CN217270640U (en) Photo-thermal enhanced organic Rankine cycle geothermal power generation system
CN215174935U (en) High-low temperature heat storage peak shaving system of thermal power plant
CN215486194U (en) Compressed air energy storage system coupled with thermal power plant
CN212108324U (en) Embedded thermal power emission reduction system for photo-thermal heat storage
CN109185085B (en) Secondary reheating type solar energy and coal-fired power plant complementary power generation system and operation method

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant