CN106016802A - Cascade CO2 heat pump capable of achieving defrosting through reversing of four-way valve and defrosting method of cascade CO2 heat pump - Google Patents
Cascade CO2 heat pump capable of achieving defrosting through reversing of four-way valve and defrosting method of cascade CO2 heat pump Download PDFInfo
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- CN106016802A CN106016802A CN201610505209.2A CN201610505209A CN106016802A CN 106016802 A CN106016802 A CN 106016802A CN 201610505209 A CN201610505209 A CN 201610505209A CN 106016802 A CN106016802 A CN 106016802A
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- conventional refrigerant
- heat exchanger
- refrigerant passage
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- 238000010257 thawing Methods 0.000 title claims abstract description 23
- 238000000034 method Methods 0.000 title claims abstract description 11
- 239000003507 refrigerant Substances 0.000 claims abstract description 127
- 238000010438 heat treatment Methods 0.000 claims abstract description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 8
- 239000006200 vaporizer Substances 0.000 claims description 10
- 238000005516 engineering process Methods 0.000 abstract description 6
- 230000007613 environmental effect Effects 0.000 abstract 1
- 125000004122 cyclic group Chemical group 0.000 description 3
- 239000002826 coolant Substances 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000009897 systematic effect Effects 0.000 description 2
- PZZOEXPDTYIBPI-UHFFFAOYSA-N 2-[[2-(4-hydroxyphenyl)ethylamino]methyl]-3,4-dihydro-2H-naphthalen-1-one Chemical compound C1=CC(O)=CC=C1CCNCC1C(=O)C2=CC=CC=C2CC1 PZZOEXPDTYIBPI-UHFFFAOYSA-N 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
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- 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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- 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
- F25B41/40—Fluid line arrangements
-
- 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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
-
- 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
- F25B2347/00—Details for preventing or removing deposits or corrosion
- F25B2347/02—Details of defrosting cycles
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses a cascade CO2 heat pump capable of achieving defrosting through reversing of a four-way valve and a defrosting method of the cascade CO2 heat pump, and belongs to heating cycle technologies of heat pumps. A conventional CO2 heat pump system cannot achieve defrosting through reversing of the four-way valve. The cascade CO2 heat pump is characterized in that a mature four-way valve reversing defrosting technology of a conventional refrigerant system is fully utilized, when a system detects that an air source evaporator needs to be defrosted, a second compressor is stopped, the CO2 heating cycle is stopped, a four-way valve of the conventional refrigerant system is controlled, the conventional refrigerant system absorbs heat from a user hot water demand side, and the frost condensed on the surface of an air source heat exchanger is removed. According to the cascade CO2 heat pump and the defrosting method, the defrosting time of a cascade CO2 system can be remarkably shortened, the defrosting efficiency of the system is improved, and a technical scheme is provided for reliable operation of the heat pump system at an extremely low environmental temperature.
Description
Technical field
The present invention relates to heat pump and heat circulating technology, particularly relate to realize the superposition type CO defrosted with cross valve commutation that one runs under extremely low ambient temperature (less than-15 DEG C)2Heat pump and superposition type CO2Defrost method.
Background technology
Due to CO2It is a few natural refrigerant without destruction several to environment, thus, thermophysical property based on its uniqueness and the CO that carries out2The research of heat pump techniques becomes the heat subject of refrigerating and air conditioning industry.Though there being many CO now2The application case row of heat pump techniques, but it is limited to some technical conditions, also have a longest segment distance from business widely, wherein typical technological difficulties are exactly CO2System defrosting problem.Existing CO2Heat pump Defrost mode, as the defrosting efficiency such as steam by-pass, electrical heating is low, particularly when heat pump runs in extremely low ambient temperature, these traditional Defrost mode effect extreme differences.For running the less conventional coolant system of pressure reduction, can be commutated defrost by cross valve, but pressure reduction is up to the CO of the 4Mpa order of magnitude2System, cross valve commutation cannot realize, on the one hand requiring the highest to the mechanical voltage endurance capability of cross valve, now almost without similar products, the vaporizer that the opposing party causes because of cross valve commutation can produce impact to system stable operation with the exchange of the role of condenser.Therefore, make full use of the cross valve commutation Defrost technology that conventional coolant system is ripe, overcome CO2Heat pump cannot be particularly important with the defect of the defrosting of cross valve reversing mode and the Defrost mode inefficiency such as steam by-pass, electrical heating.
Summary of the invention
The technical problem to be solved in the present invention is existing CO2Heat pump cannot be with the defrosting of cross valve reversing mode and the defect of the Defrost mode inefficiency such as steam by-pass, electrical heating, it is provided that a kind of superposition type CO defrosted with cross valve commutation2Heat pump and superposition type CO2Defrost method, it is ensured that CO2Heat pump reliability service under extremely low ambient temperature.
For reaching above-mentioned purpose, the superposition type CO defrosted with cross valve commutation of the present invention2Heat pump includes:
First compressor, cross valve, heat exchanger, first throttle valve, second throttle, the 3rd choke valve, evaporative condenser, the first stop valve, the second stop valve, air source heat exchanger, the second compressor, described heat exchanger has conventional refrigerant passage, hot water channel, and described evaporative condenser has conventional refrigerant passage, CO2Passage, described air source heat exchanger has conventional refrigerant passage, CO2Passage；
Described the second compressor, the CO of evaporative condenser2Passage, second throttle, the CO of air source heat exchanger2Passage connects and composes the CO of low-temperature level the most by the road2Closed circuit；
Described the first compressor, cross valve, the conventional refrigerant passage of heat exchanger, first throttle valve, the conventional refrigerant passage of evaporative condenser connect and compose the conventional refrigerant circulation circuit of high-temperature level the most by the road, in order to close or to open the conventional refrigerant passage of described evaporative condenser on the pipeline at the conventional refrigerant passage place that the first described stop valve is arranged in described evaporative condenser；The two ends of the conventional refrigerant passage of described air source heat exchanger are connected to by pipeline between conventional refrigerant passage and the cross valve of described evaporative condenser, between the conventional refrigerant passage of described heat exchanger and first throttle valve respectively and the pipeline that is connected between the conventional refrigerant passage of described heat exchanger and first throttle valve is provided with the 3rd choke valve, in order to close or to open the conventional refrigerant passage of described air source heat exchanger on the pipeline at the conventional refrigerant passage place that the second described stop valve configures described air source heat exchanger；
The conventional refrigerant passage of described heat exchanger, the conventional refrigerant passage of air source heat exchanger are exchanged as vaporizer, condenser by the commutation of described cross valve.
Preferably, the hot water channel of described heat exchanger is connected with a hot water demand side, or reversely to defrost for described air source heat exchanger from described hot water demand side draw heat with heating condition operation by the described conventional refrigerant circulation circuit of described cross valve regulation.The cold-producing medium of described conventional refrigerant circulation circuit is the one in R417A, R134a, R410A, R407c.
For reaching above-mentioned purpose, the superposition type CO of the present invention2Defrost method, described superposition type CO2Heat pump includes:
First compressor, cross valve, heat exchanger, first throttle valve, second throttle, the 3rd choke valve, evaporative condenser, the first stop valve, the second stop valve, air source heat exchanger, the second compressor, described heat exchanger has conventional refrigerant passage, hot water channel, and described evaporative condenser has conventional refrigerant passage, CO2Passage, described air source heat exchanger has conventional refrigerant passage, CO2Passage；
Described the second compressor, the CO of evaporative condenser2Passage, second throttle, the CO of air source heat exchanger2Passage connects and composes the CO of low-temperature level the most by the road2Closed circuit；
Described the first compressor, cross valve, the conventional refrigerant passage of heat exchanger, first throttle valve, the conventional refrigerant passage of evaporative condenser connect and compose the conventional refrigerant circulation circuit of high-temperature level the most by the road, in order to close or to open the conventional refrigerant passage of described evaporative condenser on the pipeline at the conventional refrigerant passage place that the first described stop valve is arranged in described evaporative condenser；The two ends of the conventional refrigerant passage of described air source heat exchanger are connected to by pipeline between conventional refrigerant passage and the cross valve of described evaporative condenser, between the conventional refrigerant passage of described heat exchanger and first throttle valve respectively and the pipeline that is connected between the conventional refrigerant passage of described heat exchanger and first throttle valve is provided with the 3rd choke valve, in order to close or to open the conventional refrigerant passage of described air source heat exchanger on the pipeline at the conventional refrigerant passage place that the second described stop valve configures described air source heat exchanger；
The conventional refrigerant passage of described heat exchanger, the conventional refrigerant passage of air source heat exchanger are exchanged as vaporizer, condenser by the commutation of described cross valve；
It is characterized in that:
When relatively low ambient temperature, open described first stop valve, start the first compressor, the second compressor, close described second stop valve, by described second compressor, the CO of evaporative condenser2Passage, second throttle, the CO of air source heat exchanger2Passage constitutes the CO of low-temperature level2Closed circuit, is made up of the conventional refrigerant circulation circuit of high-temperature level the first described compressor, cross valve, the conventional refrigerant passage of heat exchanger, first throttle valve, the conventional refrigerant passage of evaporative condenser, and system is with the CO of low-temperature level2Closed circuit runs with the endless form that heats of the conventional refrigerant circulation circuit overlapping of high-temperature level；
When higher outdoor temperature, close described first stop valve, the second compressor, open described second stop valve, be made up of the conventional refrigerant circulation circuit of high-temperature level the first described compressor, cross valve, the conventional refrigerant passage of heat exchanger, the 3rd choke valve, the conventional refrigerant passage of air source heat exchanger, system is only run with the conventional refrigerant circulation circuit of high-temperature level；
When described air source heat exchanger reach defrosting require time, close described first stop valve, close described second compressor, open described second stop valve, control the commutation of described cross valve, by described first compressor, cross valve, the conventional refrigerant passage of air source heat exchanger, 3rd choke valve, the conventional refrigerant passage of heat exchanger constitutes defrosting and heats closed circuit, the conventional refrigerant passage making described heat exchanger runs with the form of vaporizer, the conventional refrigerant passage of described air source heat exchanger runs with the form of condenser, thus remove the frost that described air source heat exchanger surface is tied.
The heat pump of the present invention includes the CO of low-temperature level2Closed circuit and the conventional refrigerant circulation circuit of high-temperature level, be operable with heating state of cyclic operation and Defrost operation operating mode, and according to the difference of outdoor environment temperature, Systematic selection heats endless form run singly to heat circulation or overlapping.Controlling cross valve commutation when need to defrost makes heat exchanger run with the form of condenser with form operation, the air source heat exchanger of vaporizer, thus remove the frost that air source heat exchanger surface is tied.
The present invention can substantially reduce superposition type CO2The defrosting time of heat pump and raising system defrosting efficiency, provide technology for heat pump reliability service under extremely low ambient temperature and ensure.
Accompanying drawing explanation
Fig. 1 is the present invention superposition type CO with cross valve commutation defrosting2The systematic schematic diagram of heat pump；
Label declaration in figure: 1-the first compressor, 2-cross valve, 3-heat exchanger, 41-first throttle valve, 42-second throttle, 43-the 3rd choke valve, 5-evaporative condenser, 61-the first stop valve, 62-the second stop valve, 7-air source heat exchanger, 8-the second compressor, 9-hot water demand side.
Detailed description of the invention
Below in conjunction with Figure of description, the present invention will be further described.
The superposition type CO defrosted with cross valve commutation of the present invention2Heat pump, as it is shown in figure 1, comprising:
First compressor 1, cross valve 2, heat exchanger 3, first throttle valve 41, second throttle the 42, the 3rd choke valve 43, evaporative condenser the 5, first stop valve the 61, second stop valve 62, air source heat exchanger the 7, second compressor 8, heat exchanger 3 there is conventional refrigerant passage, hot water channel, evaporative condenser 5 has conventional refrigerant passage, CO2Passage, air source heat exchanger 7 has conventional refrigerant passage, CO2Passage；
Second compressor 8, the CO of evaporative condenser 52Passage, second throttle 42, the CO of air source heat exchanger 72Passage connects and composes the CO of low-temperature level the most by the road2Closed circuit；
First compressor 1, cross valve 2, the conventional refrigerant passage of heat exchanger 3, first throttle valve 41, the conventional refrigerant passage of evaporative condenser 5 connect and compose the conventional refrigerant circulation circuit of high-temperature level the most by the road, in order to close or to open the conventional refrigerant passage of evaporative condenser 5 on the pipeline at the conventional refrigerant passage place that the first stop valve 61 is arranged in evaporative condenser 5；The two ends of the conventional refrigerant passage of air source heat exchanger 7 are connected between the conventional refrigerant passage of evaporative condenser 5 and cross valve 2 by pipeline respectively, between the conventional refrigerant passage of heat exchanger 3 and first throttle valve 41 and the pipeline that is connected between the conventional refrigerant passage of heat exchanger 3 and first throttle valve 41 is provided with the 3rd choke valve 43, in order to close or to open the conventional refrigerant passage of air source heat exchanger 7 on the pipeline at the conventional refrigerant passage place that the second stop valve 62 configures air source heat exchanger 7；
The conventional refrigerant passage of heat exchanger 3, the conventional refrigerant passage of air source heat exchanger 7 are exchanged as vaporizer, condenser by the commutation of cross valve 2.
First throttle valve 41 heats state of cyclic operation for regulation, and the 3rd choke valve 43 is used for regulating Defrost operation operating mode and higher room temperature condition places an order and heats state of cyclic operation, with the difference of choke valve type selecting required under distinguishing system difference operation form.
The hot water channel of heat exchanger 3 is connected with a hot water demand side 9, regulates conventional refrigerant circulation circuit by cross valve 2 and runs with heating condition or reversely defrost for air source heat exchanger 7 from hot water demand side 9 draw heat.The cold-producing medium of conventional refrigerant circulation circuit is the one in R417A, R134a, R410A, R407c.
The superposition type CO defrosted with cross valve commutation based on the invention described above2Heat pump, superposition type CO of the present invention2Defrost method is:
When relatively low ambient temperature (as when control system detects that ambient temperature is higher than-5 C), open the first stop valve 61, start first compressor the 1, second compressor 8, close the second stop valve 62, by the second compressor 8, the CO of evaporative condenser 52Passage, second throttle 42, the CO of air source heat exchanger 72Passage constitutes the CO of low-temperature level2Closed circuit, is made up of the conventional refrigerant circulation circuit of high-temperature level the first compressor 1, cross valve 2, the conventional refrigerant passage of heat exchanger 3, first throttle valve 41, the conventional refrigerant passage of evaporative condenser 5, and system is with the CO of low-temperature level2Closed circuit runs with the endless form that heats of the conventional refrigerant circulation circuit overlapping of high-temperature level；
When higher outdoor temperature (as when control system detects that ambient temperature is less than-5 C), close first stop valve the 61, second compressor 8, open the second stop valve 62, be made up of the conventional refrigerant circulation circuit of high-temperature level the first compressor 1, cross valve 2, the conventional refrigerant passage of heat exchanger 3, the 3rd choke valve 43, the conventional refrigerant passage of air source heat exchanger 7, system is only run with the conventional refrigerant circulation circuit of high-temperature level；
When air source heat exchanger 7 reaches (being detected by control system) when defrosting requires, close the first stop valve 61, close the second compressor 8, open the second stop valve 62, control cross valve 2 to commutate, by the first compressor 1, cross valve 2, the conventional refrigerant passage of air source heat exchanger 7, 3rd choke valve 43, the conventional refrigerant passage of heat exchanger 3 constitutes defrosting and heats closed circuit, the conventional refrigerant passage making heat exchanger 3 runs with the form of vaporizer, the conventional refrigerant passage of air source heat exchanger 7 runs with the form of condenser, thus remove the frost that air source heat exchanger 7 surface is tied.
Although above content combines accompanying drawing, invention has been described; but the present invention is not only limited to above-mentioned detailed description of the invention; above-mentioned detailed description of the invention is only schematically; and it is nonrestrictive; for a person skilled in the art; the technical scheme of above-mentioned enforcement example still can be modified by it, thus all made under present inventive concept any amendment, equivalents etc., within broadly falling into protection scope of the present invention.
Claims (4)
1. with the superposition type CO of cross valve commutation defrosting2Heat pump, it is characterized in that including: the first compressor (1), cross valve (2), heat exchanger (3), first throttle valve (41), second throttle (42), the 3rd choke valve (43), evaporative condenser (5), the first stop valve (61), the second stop valve (62), air source heat exchanger (7), the second compressor (8), described heat exchanger (3) has conventional refrigerant passage, hot water channel, and described evaporative condenser (5) has conventional refrigerant passage, CO2Passage, described air source heat exchanger (7) has conventional refrigerant passage, CO2Passage；
Described the second compressor (8), the CO of evaporative condenser (5)2Passage, second throttle (42), the CO of air source heat exchanger (7)2Passage connects and composes the CO of low-temperature level the most by the road2Closed circuit；
Described the first compressor (1), cross valve (2), the conventional refrigerant passage of heat exchanger (3), first throttle valve (41), the conventional refrigerant passage of evaporative condenser (5) connect and compose the conventional refrigerant circulation circuit of high-temperature level the most by the road, in order to close or to open the conventional refrigerant passage of described evaporative condenser (5) on the pipeline at the conventional refrigerant passage place that described the first stop valve (61) is arranged in described evaporative condenser (5)；The two ends of the conventional refrigerant passage of described air source heat exchanger (7) are connected between the conventional refrigerant passage of described evaporative condenser (5) and cross valve (2) by pipeline respectively, between the conventional refrigerant passage of described heat exchanger (3) and first throttle valve (41) and the pipeline that is connected between the conventional refrigerant passage of described heat exchanger (3) and first throttle valve (41) is provided with the 3rd choke valve (43), in order to close or to open the conventional refrigerant passage of described air source heat exchanger (7) on the pipeline at the conventional refrigerant passage place that described the second stop valve (62) configures described air source heat exchanger (7)；
The conventional refrigerant passage of described heat exchanger (3), the conventional refrigerant passage of air source heat exchanger (7) are exchanged as vaporizer, condenser by the commutation of described cross valve (2).
The superposition type CO defrosted with cross valve commutation the most according to claim 12Heat pump, it is characterized in that: the hot water channel of described heat exchanger (3) is connected with a hot water demand side (9), regulate described conventional refrigerant circulation circuit by described cross valve (2) and run with heating condition or reversely to defrost for described air source heat exchanger (7) from described hot water demand side (9) draw heat.
The superposition type CO defrosted with cross valve commutation the most according to claim 12Heat pump, is characterized in that: the cold-producing medium of described conventional refrigerant circulation circuit is the one in R417A, R134a, R410A, R407c.
4. superposition type CO2Defrost method, described superposition type CO2Heat pump includes:
First compressor (1), cross valve (2), heat exchanger (3), first throttle valve (41), second throttle (42), the 3rd choke valve (43), evaporative condenser (5), the first stop valve (61), the second stop valve (62), air source heat exchanger (7), the second compressor (8), described heat exchanger (3) has conventional refrigerant passage, hot water channel, and described evaporative condenser (5) has conventional refrigerant passage, CO2Passage, described air source heat exchanger (7) has conventional refrigerant passage, CO2Passage；
Described the second compressor (8), the CO of evaporative condenser (5)2Passage, second throttle (42), the CO of air source heat exchanger (7)2Passage connects and composes the CO of low-temperature level the most by the road2Closed circuit；
Described the first compressor (1), cross valve (2), the conventional refrigerant passage of heat exchanger (3), first throttle valve (41), the conventional refrigerant passage of evaporative condenser (5) connect and compose the conventional refrigerant circulation circuit of high-temperature level the most by the road, in order to close or to open the conventional refrigerant passage of described evaporative condenser (5) on the pipeline at the conventional refrigerant passage place that described the first stop valve (61) is arranged in described evaporative condenser (5)；The two ends of the conventional refrigerant passage of described air source heat exchanger (7) are connected between the conventional refrigerant passage of described evaporative condenser (5) and cross valve (2) by pipeline respectively, between the conventional refrigerant passage of described heat exchanger (3) and first throttle valve (41) and the pipeline that is connected between the conventional refrigerant passage of described heat exchanger (3) and first throttle valve (41) is provided with the 3rd choke valve (43), in order to close or to open the conventional refrigerant passage of described air source heat exchanger (7) on the pipeline at the conventional refrigerant passage place that described the second stop valve (62) configures described air source heat exchanger (7)；
The conventional refrigerant passage of described heat exchanger (3), the conventional refrigerant passage of air source heat exchanger (7) are exchanged as vaporizer, condenser by the commutation of described cross valve (2)；
It is characterized in that:
When relatively low ambient temperature, open described first stop valve (61), start the first compressor (1), the second compressor (8), close described second stop valve (62), by described second compressor (8), the CO of evaporative condenser (5)2Passage, second throttle (42), the CO of air source heat exchanger (7)2Passage constitutes the CO of low-temperature level2Closed circuit, be made up of the conventional refrigerant circulation circuit of high-temperature level described the first compressor (1), cross valve (2), the conventional refrigerant passage of heat exchanger (3), first throttle valve (41), the conventional refrigerant passage of evaporative condenser (5), system is with the CO of low-temperature level2Closed circuit runs with the endless form that heats of the conventional refrigerant circulation circuit overlapping of high-temperature level；
When higher outdoor temperature, close described first stop valve (61), the second compressor (8), open described second stop valve (62), be made up of the conventional refrigerant circulation circuit of high-temperature level described the first compressor (1), cross valve (2), the conventional refrigerant passage of heat exchanger (3), the 3rd choke valve (43), the conventional refrigerant passage of air source heat exchanger (7), system is only run with the conventional refrigerant circulation circuit of high-temperature level；
When described air source heat exchanger (7) reach defrosting require time, close described first stop valve (61), close described second compressor (8), open described second stop valve (62), control described cross valve (2) commutation, by described first compressor (1), cross valve (2), the conventional refrigerant passage of air source heat exchanger (7), 3rd choke valve (43), the conventional refrigerant passage of heat exchanger (3) constitutes defrosting and heats closed circuit, the conventional refrigerant passage making described heat exchanger (3) runs with the form of vaporizer, the conventional refrigerant passage of described air source heat exchanger (7) runs with the form of condenser, thus remove the frost that described air source heat exchanger (7) surface is tied.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610505209.2A CN106016802B (en) | 2016-07-01 | 2016-07-01 | With the superposition type CO of four-way valve commutation defrosting2Heat pump and superposition type CO2Defrost method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610505209.2A CN106016802B (en) | 2016-07-01 | 2016-07-01 | With the superposition type CO of four-way valve commutation defrosting2Heat pump and superposition type CO2Defrost method |
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| CN106016802A true CN106016802A (en) | 2016-10-12 |
| CN106016802B CN106016802B (en) | 2018-08-03 |
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| CN201610505209.2A Expired - Fee Related CN106016802B (en) | 2016-07-01 | 2016-07-01 | With the superposition type CO of four-way valve commutation defrosting2Heat pump and superposition type CO2Defrost method |
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Cited By (16)
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| CN106500380A (en) * | 2016-12-22 | 2017-03-15 | 刘勇 | It is applied to the CO of extremely cold area2Overlapping heat pump and its control method |
| CN106500381A (en) * | 2016-12-22 | 2017-03-15 | 刘勇 | It is applied to the CO of extremely cold area2Overlapping heat pump and its control method |
| CN106524552A (en) * | 2016-12-22 | 2017-03-22 | 刘勇 | CO2 cascaded heat pump system and heat pump equipment unit suitable for extremely cold area |
| CN106524275A (en) * | 2016-12-22 | 2017-03-22 | 黑龙江爱科德科技有限公司 | Compound air source heat pump heating system and circulating method |
| CN106642781A (en) * | 2016-12-22 | 2017-05-10 | 刘勇 | CO2 cascade heat pump system suitable for extremely cold areas and control method thereof |
| CN106766312A (en) * | 2016-12-22 | 2017-05-31 | 刘勇 | Suitable for the CO of extremely cold area2The heat pump and its control method of overlapping |
| CN106766308A (en) * | 2016-12-22 | 2017-05-31 | 刘勇 | Suitable for the CO of extremely cold area2Overlapping heat pump and its control method |
| CN106979638A (en) * | 2017-04-28 | 2017-07-25 | 上海理工大学 | Automobile air-conditioning evaporator defroster |
| CN107289568A (en) * | 2017-08-18 | 2017-10-24 | 广东高而美制冷设备有限公司 | A kind of strength refrigeration and the air conditioner heat pump system and its working method of quick defrost |
| CN108036557A (en) * | 2017-12-28 | 2018-05-15 | 广东芬尼克兹节能设备有限公司 | A kind of parallel connection Cascade type heat pump system |
| CN108562080A (en) * | 2018-06-22 | 2018-09-21 | 浙江正理生能科技有限公司 | A kind of air source heat pump intelligent defrosting system |
| CN111442552A (en) * | 2020-05-11 | 2020-07-24 | 珠海格力电器股份有限公司 | Cascade type refrigerant circulating system, air conditioning equipment and control method of cascade type refrigerant circulating system |
| CN114234465A (en) * | 2021-12-27 | 2022-03-25 | 上海理工大学 | High-low temperature environment test box refrigerating system adopting multi-channel evaporator |
| CN115164432A (en) * | 2022-06-27 | 2022-10-11 | 青岛海尔空调电子有限公司 | Heat pump system and control method thereof |
| CN115420039A (en) * | 2022-09-29 | 2022-12-02 | 江苏亚拓新能源科技有限公司 | Extremely cold cascade type heat pump control method |
| CN116294266A (en) * | 2023-02-27 | 2023-06-23 | 清华大学 | Air source heat pump system capable of realizing single-stage operation and cascade operation |
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| CN108562080A (en) * | 2018-06-22 | 2018-09-21 | 浙江正理生能科技有限公司 | A kind of air source heat pump intelligent defrosting system |
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| CN111442552A (en) * | 2020-05-11 | 2020-07-24 | 珠海格力电器股份有限公司 | Cascade type refrigerant circulating system, air conditioning equipment and control method of cascade type refrigerant circulating system |
| CN114234465B (en) * | 2021-12-27 | 2023-08-29 | 上海理工大学 | High-low temperature environment test box refrigerating system adopting multichannel evaporator |
| CN114234465A (en) * | 2021-12-27 | 2022-03-25 | 上海理工大学 | High-low temperature environment test box refrigerating system adopting multi-channel evaporator |
| CN115164432A (en) * | 2022-06-27 | 2022-10-11 | 青岛海尔空调电子有限公司 | Heat pump system and control method thereof |
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| CN115420039A (en) * | 2022-09-29 | 2022-12-02 | 江苏亚拓新能源科技有限公司 | Extremely cold cascade type heat pump control method |
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| CN116294266A (en) * | 2023-02-27 | 2023-06-23 | 清华大学 | Air source heat pump system capable of realizing single-stage operation and cascade operation |
| CN116294266B (en) * | 2023-02-27 | 2024-04-19 | 清华大学 | Air source heat pump system capable of realizing single-stage operation and cascade operation |
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Address after: 311241 Youyi village, Guali Town, Hangzhou City, Zhejiang Province Patentee after: Hangzhou swem New Energy Technology Development Co.,Ltd. Address before: 311241 Youyi village, Guali Town, Hangzhou City, Zhejiang Province Patentee before: HANGZHOU JIALISI WEIMU NEW ENERGY TECHNOLOGY Co.,Ltd. |
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