CN101625176A - Quasi-tertiary compressed air source hot pump system - Google Patents
Quasi-tertiary compressed air source hot pump system Download PDFInfo
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- CN101625176A CN101625176A CN200910069957A CN200910069957A CN101625176A CN 101625176 A CN101625176 A CN 101625176A CN 200910069957 A CN200910069957 A CN 200910069957A CN 200910069957 A CN200910069957 A CN 200910069957A CN 101625176 A CN101625176 A CN 101625176A
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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]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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Abstract
The invention discloses a quasi-tertiary compressed air source hot pump system, aiming at providing a hot pump system which can enhance the heating capacity of an air source hot pump and expand the application range of the air source hot pump. One path of a high pressure liquid outlet of a high pressure liquid reservoir is connected with a high temperature high pressure refrigerant inlet of an intermediate cooler, and the other path thereof is connected with an intermediate temperature intermediate pressure refrigerant inlet of the intermediate cooler; one path of a high temperature high pressure refrigerant outlet of the intermediate cooler is connected with the inlet of a flash evaporator, and the other path thereof is connected with the inlet of a stop valve; the outlet of the stop valve and the liquid outlet of the flash evaporator are paralleled followed by being paralleled with the outlet of a second electronic expansion valve followed by being connected with the inlet of a first electronic expansion valve, and the gas outlet of the flash evaporator is connected with a make-up gas opening of a low pressure level compressor. The hot pump system adds a gas supplementing system composed by the flash evaporators at the low pressure level compression part to effectively improve the working performance of the air source hot pump under the working condition of relatively low environment temperature.
Description
Technical field
The present invention relates to a kind of air source heat pump system, in particular, relate to a kind of quasi-tertiary compressed air source hot pump system.
Background technology
At present, compressed air source hot pump system is generally twin-stage.When common twin-stage compressed air source hot pump moves in the winter time, under the constant situation of condensation temperature, when outdoor environment temperature descends, along with the increase of inspiratory volume, pressure ratio increases, and pressure at expulsion increases, increase than merit, refrigerating effect per unit swept volume reduces, and unit heating capacity and heating performance coefficient all reduce, and influence the stable operation of unit.
Summary of the invention
The present invention is in order to overcome weak point of the prior art, a kind of heating capacity that can improve air source heat pump to be provided, enlarging the range of application of air source heat pump, the quasi-tertiary compressed air source hot pump system that cuts down the consumption of energy.
The present invention is achieved through the following technical solutions:
A kind of quasi-tertiary compressed air source hot pump system, it is characterized in that, comprise the low-pressure stage compressor, the hiigh pressure stage compressor, the low-pressure stage cross valve, the hiigh pressure stage cross valve, outdoor heat exchanger, indoor heat exchanger, the high pressure reservoir, flash vessel, gas-liquid separator, intercooler, first interface of low-pressure stage cross valve is connected with the outlet of low-pressure stage compressor, second interface of low-pressure stage cross valve is connected with the outlet of outdoor heat exchanger, the 3rd interface of low-pressure stage cross valve is connected with the import of gas-liquid separator, the 4th interface of low-pressure stage cross valve is connected with the 3rd interface of hiigh pressure stage cross valve, first interface of hiigh pressure stage cross valve is connected with the outlet of hiigh pressure stage compressor, be connected with the import of hiigh pressure stage compressor after the medium temperature and medium pressure refrigerant outlet parallel connection of second interface of hiigh pressure stage cross valve and intercooler, the 4th interface of hiigh pressure stage cross valve is connected with the import of indoor heat exchanger, the outlet of indoor heat exchanger is leaded up to second check valve and is connected with the import of high pressure reservoir, another road of the outlet of indoor heat exchanger is connected with the import of second electric expansion valve, the highly pressurised liquid of high pressure reservoir exports one the tunnel and is connected with the high-temperature high-pressure refrigerant import of intercooler, the highly pressurised liquid of high pressure reservoir exports another road and is connected with the medium temperature and medium pressure refrigerant inlet of intercooler by the 3rd electric expansion valve, the high-temperature high-pressure refrigerant outlet of intercooler is connected with the import of flash vessel with one the tunnel, the high-temperature high-pressure refrigerant of intercooler exports another road and is connected with the import of stop valve, be connected with the import of first electric expansion valve again with after the outlet parallel connection of second electric expansion valve after the liquid outlet parallel connection of the outlet of stop valve and flash vessel, the outlet one tunnel of first electric expansion valve is connected with the import of outdoor heat exchanger, another road of the outlet of first electric expansion valve is connected with the import of high pressure reservoir by first check valve, the gas vent of flash vessel is connected with the gas supplementing opening of low-pressure stage compressor, and the exhaust port of gas-liquid separator is connected with the import of low-pressure stage compressor.
Liquid outlet at the high pressure reservoir is connected with the device for drying and filtering import, device for drying and filtering exports one the tunnel and is connected with the high-temperature high-pressure refrigerant import of intercooler, and device for drying and filtering exports another road and is connected with the medium temperature and medium pressure refrigerant inlet of intercooler by the 3rd electric expansion valve.
Between the highly pressurised liquid outlet of the medium temperature and medium pressure refrigerant inlet of intercooler and high pressure reservoir, be connected with magnetic valve.
The present invention has following technique effect:
Heat pump of the present invention, tonifying Qi when the low-pressure stage compression section has increased an air compensating system that is made of flash vessel and is used for heat pump and heats.Obtained fully crossing cold saturated gas by what flash vessel came out, its temperature is starkly lower than compressor air suction implication body temperature degree, after gas in the gas-liquid separator mixed, temperature obviously reduced, and has reduced the delivery temperature of compressor, even under the extremely low situation of environment temperature, still can effectively improve heating capacity, improve the COP of system, can effectively improve the service behaviour of air source heat pump under the lower operating mode of environment temperature, enlarge the scope of application of air source heat pump, reduced energy consumption.
Description of drawings
Fig. 1 is the schematic diagram of quasi-tertiary compressed air source hot pump system of the present invention.
The specific embodiment
Below in conjunction with the drawings and specific embodiments to the detailed description of the invention.
Fig. 1 is the schematic diagram of quasi-tertiary compressed air source hot pump system of the present invention, comprise low-pressure stage compressor 1, hiigh pressure stage compressor 2, low-pressure stage cross valve 3, hiigh pressure stage cross valve 4, outdoor heat exchanger 5, indoor heat exchanger 6, high pressure reservoir 9, flash vessel 8, gas-liquid separator 7, intercooler 10, first interface 19 of low-pressure stage cross valve 3 is connected with the outlet of low-pressure stage compressor, second interface 20 of low-pressure stage cross valve is connected with the outlet of outdoor heat exchanger 5, the 3rd interface 21 of low-pressure stage cross valve is connected with the import of gas-liquid separator 7, the 4th interface 22 of low-pressure stage cross valve is connected with the 3rd interface 25 of hiigh pressure stage cross valve 4, first interface 23 of hiigh pressure stage cross valve is connected with the outlet of hiigh pressure stage compressor 2, be connected with the import of hiigh pressure stage compressor after second interface 24 of hiigh pressure stage cross valve and the medium temperature and medium pressure refrigerant outlet parallel connection of intercooler 10, the 4th interface 26 of hiigh pressure stage cross valve is connected with the import of indoor heat exchanger 6, the outlet of indoor heat exchanger 6 is leaded up to second check valve 16 and is connected with the import of high pressure reservoir 9, another road of the outlet of indoor heat exchanger 6 is connected with the import of second electric expansion valve 13, the highly pressurised liquid of high pressure reservoir 9 exports one the tunnel and is connected with the high-temperature high-pressure refrigerant import of intercooler 10, the highly pressurised liquid of high pressure reservoir 9 exports another road and is connected with the medium temperature and medium pressure refrigerant inlet of intercooler 10 by the 3rd electric expansion valve 14, the high-temperature high-pressure refrigerant outlet of intercooler 10 is connected with the import of flash vessel 8 with one the tunnel, the high-temperature high-pressure refrigerant of intercooler exports another road and is connected with the import of stop valve 18, be connected with the import of first electric expansion valve 12 again with after the outlet parallel connection of second electric expansion valve 13 after the liquid outlet parallel connection of the outlet of stop valve 18 and flash vessel 8, the outlet one tunnel of first electric expansion valve 12 is connected with the import of outdoor heat exchanger 5, another road of the outlet of first electric expansion valve is connected with the import of high pressure reservoir 9 by first check valve 15, the gas vent of flash vessel 8 is connected with the gas supplementing opening of low-pressure stage compressor 1, and the exhaust port of gas-liquid separator 7 is connected with the import of low-pressure stage compressor 1.
For the high pressure liquid refrigerant that the high pressure reservoir is flowed out carries out drying, liquid outlet at high pressure reservoir 9 is provided with device for drying and filtering 11, the liquid outlet of high pressure reservoir 9 is connected with device for drying and filtering 11 imports, device for drying and filtering 11 outlet one tunnel is connected with the high-temperature high-pressure refrigerant import of intercooler 10, and device for drying and filtering exports another road to be passed through the 3rd electric expansion valve 14 and be connected with the medium temperature and medium pressure refrigerant inlet of intercooler 10.
Between the highly pressurised liquid outlet of the medium temperature and medium pressure refrigerant inlet of intercooler 10 and high pressure reservoir 9, be connected with magnetic valve 17, can control the switch of bypass, when can making the coil pipe inner refrigerant, crosses when cold by the cold-producing medium in the middle cooler vessel, can close magnetic valve, otherwise, then should open magnetic valve.
Native system is opened stop valve 18 when refrigeration, first interface 19 of low-pressure stage cross valve is communicated with second interface 20, the 3rd interface 21 is communicated with the 4th interface 22, first interface 23 of hiigh pressure stage cross valve is communicated with second interface 26, the 3rd interface 26 is communicated with the 4th interface 25, and the course of work is the same with general twin-stage compressed vapour formula refrigeration system.
At heating condition, first interface 19 of low-pressure stage cross valve is communicated with the 4th interface 22, second interface 20 is communicated with the 3rd interface 21, and first interface 23 of hiigh pressure stage cross valve is communicated with the 4th interface 24, and second interface 25 is communicated with the 3rd interface 26.The gaseous refrigerant of discharging low-temp low-pressure by outdoor heat exchanger 5 enters low-pressure stage compressor 1 through low-pressure stage cross valve 3, gas-liquid separator 7, by low-pressure stage compressor 1 be collapsed into temperature higher in the attitude cold-producing medium of calming the anger, flow to hiigh pressure stage compressor 2 air intake ducts through hiigh pressure stage cross valve 4, and with the medium temperature and medium pressure refrigerant mixed of discharging by intercooler 10, mixed gaseous refrigerant enters hiigh pressure stage compressor 2, be compressed into high temperature and high pressure gaseous refrigerant, enter indoor heat exchanger 6 through hiigh pressure stage cross valve 4 again, with the room air heat exchange, reach and heat purpose.The refrigerant vapour of HTHP becomes cryogenic high pressure liquid in this cooling, condensation, enters in the high pressure receiver 9 by second check valve 16 again.High pressure liquid refrigerant by high pressure receiver 9 outflows, sub-fraction enters the medium temperature and medium pressure coolant channel of intercooler through magnetic valve 17, the 3rd electric expansion valve 14, most of high pressure liquid refrigerant intercooler high-temperature high-pressure refrigerant passage of flowing through absorbs the evaporation latent heat of medium temperature and medium pressure coolant channel inner refrigerant and realizes significantly cold excessively.Enter flash vessel 8 then, the cold-producing medium that is evaporated to gaseous state in flash vessel 8 enters low-pressure stage compressor 1 and finishes the tonifying Qi process.The cold fully excessively high pressure liquid refrigerant that obtains of discharging from flash vessel 8 lower ends mixes with the gaseous refrigerant that flows out from second electric expansion valve, through heat become with the 12 throttling step-downs of first electric expansion valve in the liquid state of warm low pressure, the inlet chamber external heat exchanger 5 again, the heat of vaporization of absorption chamber outer air becomes the gaseous refrigerant of low-temp low-pressure, the low-pressure stage of flowing through again cross valve 3, gas-liquid separator 7 return the low-pressure stage compressor, finish heating circulation.First check valve 15 is installed, and the low temperature high pressure gas that can prevent to be come out by indoor heat exchanger is without the direct inlet chamber external heat exchanger of intercooler, thereby can't carry out tonifying Qi.
Although relate to a kind of quasi-tertiary compressed air source hot pump system and carried out special description disclosed with reference to embodiment, embodiment described above is illustrative and not restrictive, under the situation that does not break away from the spirit and scope of the present invention, all variations and modification are all within the scope of the present invention.
Claims (3)
1, a kind of quasi-tertiary compressed air source hot pump system, it is characterized in that, comprise the low-pressure stage compressor, the hiigh pressure stage compressor, the low-pressure stage cross valve, the hiigh pressure stage cross valve, outdoor heat exchanger, indoor heat exchanger, the high pressure reservoir, flash vessel, gas-liquid separator, intercooler, first interface of low-pressure stage cross valve is connected with the outlet of low-pressure stage compressor, second interface of low-pressure stage cross valve is connected with the outlet of outdoor heat exchanger, the 3rd interface of low-pressure stage cross valve is connected with the import of gas-liquid separator, the 4th interface of low-pressure stage cross valve is connected with the 3rd interface of hiigh pressure stage cross valve, first interface of hiigh pressure stage cross valve is connected with the outlet of hiigh pressure stage compressor, be connected with the import of hiigh pressure stage compressor after the medium temperature and medium pressure refrigerant outlet parallel connection of second interface of hiigh pressure stage cross valve and intercooler, the 4th interface of hiigh pressure stage cross valve is connected with the import of indoor heat exchanger, the outlet of indoor heat exchanger is leaded up to second check valve and is connected with the import of high pressure reservoir, another road of the outlet of indoor heat exchanger is connected with the import of second electric expansion valve, the highly pressurised liquid of high pressure reservoir exports one the tunnel and is connected with the high-temperature high-pressure refrigerant import of intercooler, the highly pressurised liquid of high pressure reservoir exports another road and is connected with the medium temperature and medium pressure refrigerant inlet of intercooler by the 3rd electric expansion valve, the high-temperature high-pressure refrigerant of intercooler exports one the tunnel and is connected with the import of flash vessel, the high-temperature high-pressure refrigerant of intercooler exports another road and is connected with the import of stop valve, be connected with the import of first electric expansion valve again with after the outlet parallel connection of second electric expansion valve after the liquid outlet parallel connection of the outlet of stop valve and flash vessel, the outlet one tunnel of first electric expansion valve is connected with the import of outdoor heat exchanger, another road of the outlet of first electric expansion valve is connected with the import of high pressure reservoir by first check valve, the gas vent of flash vessel is connected with the gas supplementing opening of low-pressure stage compressor, and the exhaust port of gas-liquid separator is connected with the import of low-pressure stage compressor.
2, quasi-tertiary compressed air source hot pump system according to claim 1, it is characterized in that, the liquid outlet of high pressure reservoir is connected with the device for drying and filtering import, device for drying and filtering exports one the tunnel and is connected with the high-temperature high-pressure refrigerant import of intercooler, and device for drying and filtering exports another road and is connected with the medium temperature and medium pressure refrigerant inlet of intercooler by the 3rd electric expansion valve.
3, quasi-tertiary compressed air source hot pump system according to claim 1 is characterized in that, is connected with magnetic valve between the highly pressurised liquid outlet of the medium temperature and medium pressure refrigerant inlet of intercooler and high pressure reservoir.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2009100699570A CN101625176B (en) | 2009-07-30 | 2009-07-30 | Quasi-tertiary compressed air source hot pump system |
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| CN2009100699570A CN101625176B (en) | 2009-07-30 | 2009-07-30 | Quasi-tertiary compressed air source hot pump system |
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| CN101625176B CN101625176B (en) | 2011-01-19 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102331112A (en) * | 2011-09-20 | 2012-01-25 | 王正鹏 | Heat pump working condition system |
| CN102620463A (en) * | 2012-03-27 | 2012-08-01 | 美的集团有限公司 | Novel low-temperature strong-heat multi-split air conditioning system |
| CN103423919A (en) * | 2012-05-23 | 2013-12-04 | 约克广州空调冷冻设备有限公司 | Air-source heat pump system and defrosting and draining method for same |
| CN103649650A (en) * | 2011-07-05 | 2014-03-19 | 开利公司 | Refrigeration circuit, gas-liquid separator and heating and cooling system |
| CN107514830A (en) * | 2016-06-18 | 2017-12-26 | 上海春至新能源科技有限公司 | A kind of single multi-stage compression automatic conversion Multifunctional heat pump system |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN201014625Y (en) * | 2007-03-23 | 2008-01-30 | 大连中星科技开发有限公司 | Winter household air source heat pump heating system and device for north cold area |
| CN201028858Y (en) * | 2007-04-12 | 2008-02-27 | 武汉新世界制冷工业有限公司 | Double-unit two-stage screw type refrigerant compressor unit |
| CN101457949B (en) * | 2007-12-13 | 2011-09-21 | 大连中星科技开发有限公司 | Domestic air source heat pump heating system |
| CN201225784Y (en) * | 2008-05-16 | 2009-04-22 | 大连冷冻机股份有限公司 | Heat pump plant unit |
| CN101387456B (en) * | 2008-10-31 | 2010-06-02 | 大连理工大学 | Cold-warmer bath integrated air source heat pump at cold region |
| CN201463395U (en) * | 2009-07-30 | 2010-05-12 | 天津商业大学 | Two-stage compressed air source heat pump system with air supplement function |
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2009
- 2009-07-30 CN CN2009100699570A patent/CN101625176B/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103649650A (en) * | 2011-07-05 | 2014-03-19 | 开利公司 | Refrigeration circuit, gas-liquid separator and heating and cooling system |
| CN103649650B (en) * | 2011-07-05 | 2015-07-22 | 开利公司 | Refrigeration circuit, gas-liquid separator and heating and cooling system |
| CN102331112A (en) * | 2011-09-20 | 2012-01-25 | 王正鹏 | Heat pump working condition system |
| CN102620463A (en) * | 2012-03-27 | 2012-08-01 | 美的集团有限公司 | Novel low-temperature strong-heat multi-split air conditioning system |
| CN103423919A (en) * | 2012-05-23 | 2013-12-04 | 约克广州空调冷冻设备有限公司 | Air-source heat pump system and defrosting and draining method for same |
| CN103423919B (en) * | 2012-05-23 | 2016-06-29 | 约克广州空调冷冻设备有限公司 | Air source heat pump system and the defrost fluid-discharge method for this air source heat pump system |
| CN107514830A (en) * | 2016-06-18 | 2017-12-26 | 上海春至新能源科技有限公司 | A kind of single multi-stage compression automatic conversion Multifunctional heat pump system |
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| CN101625176B (en) | 2011-01-19 |
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Granted publication date: 20110119 Termination date: 20130730 |