CN105042672A - Air source CO2 heat pump system suitable for connecting heating radiators - Google Patents
Air source CO2 heat pump system suitable for connecting heating radiators Download PDFInfo
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- CN105042672A CN105042672A CN201510553199.5A CN201510553199A CN105042672A CN 105042672 A CN105042672 A CN 105042672A CN 201510553199 A CN201510553199 A CN 201510553199A CN 105042672 A CN105042672 A CN 105042672A
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- heat
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- heating
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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
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
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Abstract
The invention relates to an air source CO2 heat pump system suitable for connecting heating radiators. The heat pump system comprises an air source transcritical CO2 heat pump system, a heat recovery system and a heating circulation system. The air source transcritical CO2 heat pump system is mainly formed by sequentially connecting a CO2 high-pressure compressor, a gas cooler, a thermal recoverer, a first electronic expansion valve and a fin type heat exchanger through a pipeline in series. The thermal recovery system is mainly formed by sequentially connecting a compressor, a condenser, a second electronic expansion valve and a thermal recoverer through a pipeline in series. A pipeline of the heating circulation system is further connected with the condenser and the gas cooler. The system can be used for circulation heating in winter, the return water supply temperature reaches 70 DEG C/50 DEG C, and COP reaches 2.0 at the environment temperature of -20 DEG C. The heating radiators can be arranged at the tail heating end. The system solves the congenital problem that a pure air source transcritical CO2 heat pump system is low in heating efficiency, and meanwhile the maximum utilization of an air heat source is achieved.
Description
Technical field
The present invention relates to a kind of air-source CO being suitable for connecing radiator
2heat pump, this system is applicable to high return water temperature, can meet the heating air-source CO of radiator
2heat pump, when high return water temperature (more than 50 DEG C), still efficiently can heat heating.
Background technology
Be different from conventional refrigerant heat pump circulating system, air-source Trans-critical cycle CO
2the height of heat pump gas cooler exit temperature determines the height of systematic energy efficiency ratio, and the size of gas cooler exit temperature is when gas cooler heat exchange area is determined, gas cooler water side inflow temperature is then play material important parameter to it.Therefore, air-source Trans-critical cycle CO in principle
2heat pump is not suitable for the thermal source as heat supply in winter, but due to its cold-producing medium be environmentally friendly, when running at low temperatures simultaneously, air-source Trans-critical cycle CO
2the relative conventional heat pump of heat pump has the advantage of higher energy efficiency ratio, for realizing energy saving standard requirement, being necessary while utilizing this system advantage, can effectively making full use of it again and absorbing heat, therefore have developed a kind of air-source CO being suitable for connecing radiator
2heat pump, to realize in environment temperature-20 DEG C of situations, meets heating radiator required for backwater temperature 70/50 DEG C even temperature requirements of requirements at the higher level.
Summary of the invention
The object of this invention is to provide and do not needing, under the prerequisite to indoor heating terminal transformation, to provide a kind of air-source CO being suitable for directly docking radiator
2heat pump, realizes at environment temperature-20 DEG C, and supply and return water temperature can be provided to reach 70 DEG C/50 DEG C, the indoor energy-saving heating that systematic energy efficiency ratio is greater than 2.0.
Above-mentioned purpose is achieved through the following technical solutions:
A kind ofly be suitable for the air-source CO connecing radiator
2heat pump, this heat pump comprises air-source Trans-critical cycle CO
2heat pump, heat recovery system and the heating circulatory system three part; Described air-source Trans-critical cycle CO
2heat pump is primarily of CO
2high pressure compressor, gas cooler, heat regenerator, the first electric expansion valve and finned heat exchanger group to be contacted composition successively by pipeline, described heat recovery system to be contacted composition by pipeline successively primarily of compressor, condenser, the second electric expansion valve and heat regenerator, meanwhile, the pipeline of the described heating circulatory system also connects successively condenser and gas cooler (is connected condenser and gas cooler be also connected in heat in the circulatory system) simultaneously.
Described air-source Trans-critical cycle CO
2coupling is carried out by heat regenerator between heat pump and heat recovery system; The recirculated water of the heating circulatory system is successively by heat recovery system condenser and air-source Trans-critical cycle CO
2the gas cooler of heat pump carries out twice heating, realizes the heat that return water temperature absorbs two heat exchangers, the supply water temperature required for gradient-heated to room heater sheet, realizes heat user heating requirement.
Above-mentionedly be suitable for the air-source CO connecing radiator
2heat pump, this heat pump is primarily of CO
2the compositions such as high pressure compressor, gas cooler, heat regenerator, finned heat exchanger group, compressor, condenser, water circulating pump, the first and second electric expansion valves and pipeline.
Air-source Trans-critical cycle CO
2heat pump is primarily of CO
2the parts such as high pressure compressor, gas cooler, heat regenerator, the first electric expansion valve, finned heat exchanger group form, and to be contacted successively formation closed circulation system by pipeline between them, the working medium adopted in this system is CO
2gas, the first electric expansion valve is High Pressure Difference electric expansion valve (height pressure reduction is not less than 40bar).In finned heat exchanger group, the CO of low-temp low-pressure two phase
2after absorbing ambient air outside heat, form the CO with certain degree of superheat
2gas; Then this CO
2gas passes through CO
2the supercritical CO of high pressure compressor boil down to HTHP
2gas, heats heat supply backwater to heating demands temperature in gas cooler; Then still there is the CO of uniform temperature
2gas enters heat regenerator, and the thermal source as heat recovery system evaporimeter releases heat, forms high pressure low temperature CO
2; Finally by the first electric expansion valve, throttling forms the CO of low-temp low-pressure two phase
2enter finned heat exchanger group, complete a circulation process of heat absorption and release.
Heat recovery system is primarily of parts compositions such as conventional refrigerant compressor, condenser, the second electric expansion valve, heat regenerators, to be contacted successively formation closed circulation system by pipeline between them, the working medium adopted in this system is conventional refrigerant, the Prof. Du Yucang such as preferred R-134a, R-410A have certain environmental protection characteristic and the stable cold-producing medium of physical property, and the second electric expansion valve is conventional refrigerant system electric expansion valve.In heat regenerator, the low-temp low-pressure conventional refrigerant that system adopts absorbs and flows through air-source Trans-critical cycle CO
2the supercritical CO still with uniform temperature after heat pump gas cooler
2heat entrained by gas, the refrigerant gas gasified as having certain degree of superheat; Then boil down to high-temperature high-pressure refrigerant gas in conventional refrigerant compressor, release heat heating circulatory system backwater in condenser, after being condensed into the liquid refrigerant with certain degree of supercooling, by the throttling of conventional refrigerant system electric expansion valve, enter into heat regenerator, complete the circulatory function of heat recovery and heating circulatory system backwater.
The described heating circulatory system to be contacted composition by pipeline successively primarily of condenser, gas cooler, water circulating pump and heat user end-equipment.Heat user end-equipment, heat recovery system condenser, air-source Trans-critical cycle CO
2to be contacted successively formation closed circulation system by pipeline between the parts such as heat pump gas cooler, water circulating pump.Heating system backwater is successively through heat recovery system condenser and air-source Trans-critical cycle CO
2heat pump gas cooler is heated to the heating and supplying water temperature of demand for twice, is pumped to heat user heating terminal equipment through water circulating pump, realizes heat user heating demands.
In system of the present invention, air-source Trans-critical cycle CO
2heat pump achieves Cryogenic air side draught and receives heat, by gas cooler heat cycles hot water with by the function of heat regenerator to heat recovery system heat release; Air-source Trans-critical cycle CO
2heat pump and heat recovery system carry out coupling by heat regenerator; Heat recovery system absorbs air-source Trans-critical cycle CO by heat regenerator
2the partial heat of heat pump, by condenser heat rejection to circulating hot water.Heating system recirculated water is by heat recovery system condenser and air-source Trans-critical cycle CO
2heat pump gas cooler heats at twice, realizes heat user heating requirement.This system overcomes simple air-source Trans-critical cycle CO
2heat pump is used for the low congenital problem of heat supply efficiency, also achieves the maximization that air heat source utilizes simultaneously.
Of the present inventionly be suitable for the air-source CO connecing radiator
2heat pump can be used for circulating-heating heating in winter, and supply and return water temperature reaches 70 DEG C/50 DEG C, and under the environment temperature of-20 DEG C, COP reaches 2.0; Heating end directly can use radiator.
Accompanying drawing explanation
Fig. 1 is a kind of air-source CO being suitable for connecing radiator of the present invention
2the structural representation of heat pump.
Main Reference Numerals:
A air-source Trans-critical cycle CO
2heat pump
B heat recovery system
C heats the circulatory system
1CO
2high pressure compressor 2 gas cooler
3 heat regenerator 4 first electric expansion valves
5 finned heat exchanger group 6 conventional refrigerant compressors
7 condenser 8 second electric expansion valves
9 hot-water circulating pumps
Detailed description of the invention
As shown in Figure 1, a kind ofly the air-source CO connecing radiator is suitable for for of the present invention
2the structural representation of heat pump and systematic schematic diagram.This system comprises air-source Trans-critical cycle CO
2heat pump A, heat recovery system B and heating circulatory system C tri-parts, comprise CO
2the parts such as high pressure compressor 1, gas cooler 2, heat regenerator 3, finned heat exchanger group 5, conventional refrigerant compressor 6, condenser 7, hot-water circulating pump 9, first electric expansion valve 4, second electric expansion valve 8 and pipeline.Air-source Trans-critical cycle CO
2heat pump A and heat recovery system B carries out coupling by heat regenerator; The pipeline of heating circulatory system C also connects condenser 7 and gas cooler 2 successively, and the recirculated water of heating circulatory system C is successively by condenser 7 and the air-source Trans-critical cycle CO of heat recovery system B
2the gas cooler 2 of heat pump A carries out twice heating, realizes the heat that return water temperature absorbs two heat exchangers, the supply water temperature required for gradient-heated to room heater sheet, realizes heat user heating requirement.
Air-source Trans-critical cycle CO
2heat pump A is primarily of CO
2the parts such as high pressure compressor 1, gas cooler 2, heat regenerator 3, first electric expansion valve 4, finned heat exchanger group 5 connect to form successively.First electric expansion valve 4 is High Pressure Difference electric expansion valve, and height pressure reduction is higher than 40 bar (bar).In finned heat exchanger group 5, the CO of low-temp low-pressure two phase
2after absorbing ambient air outside heat, form the CO with certain degree of superheat
2gas; Then CO
2gas passes through high pressure CO
2the supercritical CO of compressor 1 boil down to HTHP
2gas; The supercritical CO of HTHP in gas cooler 2
2air release heat heating recirculated water, the condenser 7 through heat recovery system B is heated heating circulating water heating once to temperature to Tm to Th, this temperature is heating system end-equipment demand temperature; Then still there is the CO of uniform temperature
2gas enters heat regenerator 3, and the thermal source as heat recovery system evaporimeter releases heat, forms high pressure low temperature CO
2; Finally by the first electric expansion valve 4, throttling forms the CO of low-temp low-pressure two phase
2enter finned heat exchanger group 5, complete a circulation process of heat absorption and release.
Heat recovery system B is connected to form successively by parts such as conventional refrigerant compressor 6, condenser 7, second electric expansion valve 8, heat regenerators 3.In heat regenerator 3, the low-temp low-pressure conventional refrigerant (as R134a, R410a etc.) that system adopts absorbs and flows through air-source Trans-critical cycle CO
2the supercritical CO still with uniform temperature after heat pump gas cooler 2
2heat entrained by gas, the refrigerant gas gasified as having certain degree of superheat; Then boil down to high-temperature high-pressure refrigerant gas in conventional refrigerant compressor 6, in condenser 7, release heat heating circulatory system C backwater is to temperature Tm, simultaneously condensation of refrigerant is after the liquid state with certain degree of supercooling, by the second electric expansion valve 8 throttling, enter into heat regenerator 3, complete the function of heat recovery and heating circulatory system backwater.
Circulatory system C is primarily of heat user end-equipment, heat recovery system condenser 7, air-source Trans-critical cycle CO in heating
2the parts such as heat pump gas cooler 2, water circulating pump 9 connect to form successively.In heating system, heating circulating backwater is heated to Tm through heat recovery system condenser 7 first time, then enters into air-source Trans-critical cycle CO
2again be heated to Th in heat pump gas cooler 2, Th is heating system demand temperature; And after be pumped to heat user through heating system circulating pump 9, realize heating demands.
Originally the air-source CO connecing radiator is suitable for
2heat pump can be used for circulating-heating heating in winter, and supply and return water temperature can realize 70 DEG C/50 DEG C, and under the environment temperature of-20 DEG C, COP reaches 2.0; Heating end can adopt radiator form, without the need to transforming original heating system.
Claims (9)
1. one kind is suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: this heat pump comprises air-source Trans-critical cycle CO
2heat pump, heat recovery system and the heating circulatory system; Described air-source Trans-critical cycle CO
2heat pump is primarily of CO
2high pressure compressor, gas cooler, heat regenerator, the first electric expansion valve and finned heat exchanger group to be contacted composition successively by pipeline, described heat recovery system to be contacted composition by pipeline successively primarily of compressor, condenser, the second electric expansion valve and heat regenerator, and the pipeline of the described heating circulatory system also connects condenser and gas cooler.
2. be according to claim 1ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: the described heating circulatory system to be contacted composition by pipeline successively primarily of condenser, gas cooler, water circulating pump and heat user end-equipment.
3. be according to claim 1ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: described air-source Trans-critical cycle CO
2the working medium that heat pump adopts is CO
2gas.
4. be according to claim 1ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: the first electric expansion valve is High Pressure Difference electric expansion valve.
5. be according to claim 1ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: described air-source Trans-critical cycle CO
2in heat pump, the CO of low-temp low-pressure two phase in finned heat exchanger group
2after absorbing ambient air outside heat, pass through CO
2the supercritical CO of high pressure compressor boil down to HTHP
2gas, heats heat supply backwater to heating demands temperature in gas cooler; Then still there is the CO of uniform temperature
2gas enters heat regenerator, and the thermal source as heat recovery system evaporimeter releases heat, forms high pressure low temperature CO
2; Finally by the first electric expansion valve, throttling forms the CO of low-temp low-pressure two phase
2enter finned heat exchanger group, complete a circulation process of heat absorption and release.
6. be according to claim 1ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: the working medium that described heat recovery system adopts is conventional refrigerant.
7. be according to claim 6ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: described conventional refrigerant is R-134a or R-410A.
8. be according to claim 7ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: in described heat recovery system, and the low-temp low-pressure conventional refrigerant that system adopts in heat regenerator absorbs and flows through air-source Trans-critical cycle CO
2the supercritical CO still with uniform temperature after heat pump gas cooler
2heat entrained by gas, the refrigerant gas gasified as having certain degree of superheat; Then boil down to high-temperature high-pressure refrigerant gas in compressor, release heat heating circulatory system backwater in condenser, after being condensed into the liquid refrigerant with certain degree of supercooling, by the second electric expansion valve throttling, enter into heat regenerator, complete the circulatory function of heat recovery and heating circulatory system backwater.
9. be according to claim 1ly suitable for the air-source CO connecing radiator
2heat pump, is characterized in that: the backwater of the described heating circulatory system is successively through condenser and the air-source Trans-critical cycle CO of heat recovery system
2the gas cooler of heat pump is heated to the heating and supplying water temperature of demand for twice, is pumped to heat user heating terminal equipment through water circulating pump.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510553199.5A CN105042672A (en) | 2015-09-01 | 2015-09-01 | Air source CO2 heat pump system suitable for connecting heating radiators |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510553199.5A CN105042672A (en) | 2015-09-01 | 2015-09-01 | Air source CO2 heat pump system suitable for connecting heating radiators |
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| Publication Number | Publication Date |
|---|---|
| CN105042672A true CN105042672A (en) | 2015-11-11 |
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ID=54449448
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510553199.5A Pending CN105042672A (en) | 2015-09-01 | 2015-09-01 | Air source CO2 heat pump system suitable for connecting heating radiators |
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Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106196683A (en) * | 2016-08-10 | 2016-12-07 | 燕园德普科技（北京）有限公司 | A kind of super low temperature heat pump system for heating and control method thereof |
| CN107676845A (en) * | 2017-10-26 | 2018-02-09 | 何铭 | A kind of CO2Air source heat pump synergy heating installation |
| CN108105833A (en) * | 2018-01-31 | 2018-06-01 | 天津商业大学 | CO is subcooled in a kind of mechanical assistance2Trans-critical cycle heat pump heating system |
| CN108180667A (en) * | 2018-01-31 | 2018-06-19 | 天津商业大学 | CO is subcooled in a kind of mechanical-assisted2Trans-critical cycle cooling and warming integral system |
| CN108180666A (en) * | 2018-01-31 | 2018-06-19 | 天津商业大学 | CO is subcooled in a kind of non-azeotropic working medium mechanical-assisted2Cooling and warming integral system |
| CN108317581A (en) * | 2018-01-31 | 2018-07-24 | 天津商业大学 | A kind of non-azeotropic working medium mechanical-assisted supercooling CO2Trans-critical cycle heat pump heating system |
| CN108458512A (en) * | 2018-03-13 | 2018-08-28 | 中铁工程设计咨询集团有限公司 | A kind of carbon dioxide air source heat pump system |
| CN109374322A (en) * | 2018-09-27 | 2019-02-22 | 合肥通用机械研究院有限公司 | A kind of water cooler test device of calibration tape heat recovery function |
| CN111174456A (en) * | 2020-03-06 | 2020-05-19 | 吉风环境科技(江苏)有限公司 | Split overlapping type CO2Air source heat pump unit |
| CN111271752A (en) * | 2020-02-14 | 2020-06-12 | 同济大学 | Multi-heat exchanger serial transcritical CO2Heat pump heating system |
| CN111336707A (en) * | 2020-02-29 | 2020-06-26 | 同济大学 | Carbon dioxide heat pump heating system with topologic homoembryo circulation |
| CN111750525A (en) * | 2020-05-28 | 2020-10-09 | 河南省中能联建地热工程有限公司 | Double-source hot water unit based on air source and water source double heat sources |
| CN111795423A (en) * | 2020-03-26 | 2020-10-20 | 同济大学 | Carbon dioxide heat pump heating system based on three-fluid heat exchanger |
| CN113357692A (en) * | 2021-06-04 | 2021-09-07 | 中国科学院广州能源研究所 | Circulating water waste heat recovery system of thermal power plant |
| CN113739419A (en) * | 2021-09-26 | 2021-12-03 | 上海智楹机器人科技有限公司 | Waste heat recovery type household intelligent kitchen waste disposer |
| CN113865149A (en) * | 2021-08-30 | 2021-12-31 | 浙江工业大学 | Composite heat pump system for killing new coronavirus at high temperature |
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Cited By (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106196683A (en) * | 2016-08-10 | 2016-12-07 | 燕园德普科技（北京）有限公司 | A kind of super low temperature heat pump system for heating and control method thereof |
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| CN108105833A (en) * | 2018-01-31 | 2018-06-01 | 天津商业大学 | CO is subcooled in a kind of mechanical assistance2Trans-critical cycle heat pump heating system |
| CN108180667A (en) * | 2018-01-31 | 2018-06-19 | 天津商业大学 | CO is subcooled in a kind of mechanical-assisted2Trans-critical cycle cooling and warming integral system |
| CN108180666A (en) * | 2018-01-31 | 2018-06-19 | 天津商业大学 | CO is subcooled in a kind of non-azeotropic working medium mechanical-assisted2Cooling and warming integral system |
| CN108317581A (en) * | 2018-01-31 | 2018-07-24 | 天津商业大学 | A kind of non-azeotropic working medium mechanical-assisted supercooling CO2Trans-critical cycle heat pump heating system |
| CN108458512A (en) * | 2018-03-13 | 2018-08-28 | 中铁工程设计咨询集团有限公司 | A kind of carbon dioxide air source heat pump system |
| CN111595603A (en) * | 2018-09-27 | 2020-08-28 | 合肥通用机械研究院有限公司 | Improved testing device for testing water chilling unit with heat recovery function |
| CN109374322B (en) * | 2018-09-27 | 2020-07-07 | 合肥通用机械研究院有限公司 | Water chilling unit testing device with heat recovery function |
| CN109374322A (en) * | 2018-09-27 | 2019-02-22 | 合肥通用机械研究院有限公司 | A kind of water cooler test device of calibration tape heat recovery function |
| CN111595603B (en) * | 2018-09-27 | 2021-12-14 | 合肥通用机械研究院有限公司 | Improved testing device for testing water chilling unit with heat recovery function |
| CN111271752A (en) * | 2020-02-14 | 2020-06-12 | 同济大学 | Multi-heat exchanger serial transcritical CO2Heat pump heating system |
| CN111336707A (en) * | 2020-02-29 | 2020-06-26 | 同济大学 | Carbon dioxide heat pump heating system with topologic homoembryo circulation |
| CN111174456A (en) * | 2020-03-06 | 2020-05-19 | 吉风环境科技(江苏)有限公司 | Split overlapping type CO2Air source heat pump unit |
| CN111795423A (en) * | 2020-03-26 | 2020-10-20 | 同济大学 | Carbon dioxide heat pump heating system based on three-fluid heat exchanger |
| CN111750525A (en) * | 2020-05-28 | 2020-10-09 | 河南省中能联建地热工程有限公司 | Double-source hot water unit based on air source and water source double heat sources |
| CN113357692A (en) * | 2021-06-04 | 2021-09-07 | 中国科学院广州能源研究所 | Circulating water waste heat recovery system of thermal power plant |
| CN113865149A (en) * | 2021-08-30 | 2021-12-31 | 浙江工业大学 | Composite heat pump system for killing new coronavirus at high temperature |
| CN113739419A (en) * | 2021-09-26 | 2021-12-03 | 上海智楹机器人科技有限公司 | Waste heat recovery type household intelligent kitchen waste disposer |
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Inventor after: Wang Shouguo Inventor after: Hong Wei Inventor after: Xue Qiang Inventor after: Yu Xiaoying Inventor after: Lin Shihua Inventor after: Chen Qiong Inventor after: Shui Chunyu Inventor before: Hong Wei Inventor before: Wang Shouguo Inventor before: Xue Qiang Inventor before: Yu Xiaoying |
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Application publication date: 20151111 |