CN111550943A - Secondary throttling double-condensation refrigerating system, air conditioner and control method - Google Patents
Secondary throttling double-condensation refrigerating system, air conditioner and control method Download PDFInfo
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- CN111550943A CN111550943A CN202010338284.0A CN202010338284A CN111550943A CN 111550943 A CN111550943 A CN 111550943A CN 202010338284 A CN202010338284 A CN 202010338284A CN 111550943 A CN111550943 A CN 111550943A
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- 238000009833 condensation Methods 0.000 title claims abstract description 53
- 238000000034 method Methods 0.000 title claims abstract description 13
- 238000005057 refrigeration Methods 0.000 claims abstract description 74
- 239000003507 refrigerant Substances 0.000 claims abstract description 60
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 104
- 230000006835 compression Effects 0.000 claims description 103
- 238000007906 compression Methods 0.000 claims description 103
- 230000005494 condensation Effects 0.000 claims description 21
- 238000001816 cooling Methods 0.000 claims description 13
- 230000009977 dual effect Effects 0.000 claims description 3
- 238000010438 heat treatment Methods 0.000 abstract description 31
- 230000004087 circulation Effects 0.000 abstract description 26
- 238000001704 evaporation Methods 0.000 abstract description 15
- 230000008020 evaporation Effects 0.000 abstract description 15
- 238000004781 supercooling Methods 0.000 abstract description 11
- 238000010586 diagram Methods 0.000 description 15
- 239000000498 cooling water Substances 0.000 description 8
- 238000010521 absorption reaction Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 238000005265 energy consumption Methods 0.000 description 3
- 230000017525 heat dissipation Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000001502 supplementing effect Effects 0.000 description 3
- 125000004122 cyclic group Chemical group 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000001172 regenerating effect Effects 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000007306 turnover Effects 0.000 description 1
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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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B31/00—Compressor arrangements
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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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
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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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B41/30—Expansion means; Dispositions thereof
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
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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
- F25B2500/00—Problems to be solved
- F25B2500/31—Low ambient temperatures
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- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides a secondary throttling double-condensation refrigeration system, an air conditioner and a control method. Compared with a primary throttling refrigeration cycle system, the secondary throttling refrigeration cycle system has the advantages that the latent heat and the sensible heat of the refrigerant after primary throttling are released by the secondary condenser under the condition of the same evaporation pressure, superheat degree, supercooling degree and refrigerant circulation quantity, and the heating quantity, the refrigerating quantity, the heating performance coefficient and the refrigerating performance coefficient of the system are greatly improved.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to a secondary throttling double-condensation refrigeration system, an air conditioner and a control method.
Background
In the prior art, the air conditioner has a large proportion of energy consumption in total building energy consumption, and the trend of the air conditioner industry is about how to further improve the performance coefficient of the air conditioner and reduce the energy consumption of the air conditioner. The conventional primary throttling refrigeration cycle system has the defects of limited evaporation pressure and condensation pressure, small refrigerating capacity and heating capacity, low compression power consumption and difficult further improvement of the performance coefficient of the system. The once throttling refrigeration cycle adopts once throttling, and the throttling degree of the cycle mode is limited, so that the evaporation temperature cannot reach the low-temperature working condition, and the system cannot adapt to heating under the low-temperature working condition. In addition, a single condenser is adopted in the primary throttling refrigeration cycle system, so that the condensing pressure, the cooling water outlet temperature and the cooling air outlet temperature are single, the system function is single, and the diversification is insufficient.
The air conditioner in the prior art has the problems that a primary throttling refrigeration circulating system is influenced by the temperature of inflow water, the condensing pressure is insufficient, and the heating capacity is small; the primary throttling refrigeration cycle system has the problems of high evaporation pressure, small evaporation temperature difference and small heat absorption refrigeration capacity; the temperature range of the operating environment of the primary throttling refrigeration cycle system is small, and the primary throttling refrigeration cycle system cannot adapt to the heating under the working condition of low environment temperature; the problem of low performance coefficient of the primary throttling refrigeration cycle system; the invention discloses a secondary throttling double-condensation refrigeration system, an air conditioner and a control method, and solves the technical problems that the condensation pressure, the water outlet temperature and the air outlet temperature of a primary throttling refrigeration cycle system are single, so that the system function is single and the like.
Disclosure of Invention
Therefore, the technical problem to be solved by the present invention is to overcome the defect that the air conditioner in the prior art has the problem of low heating/cooling performance coefficient of the primary throttling refrigeration cycle system, so as to provide a secondary throttling dual-condensation refrigeration system, an air conditioner and a control method.
In order to solve the above problems, the present invention provides a secondary throttling dual-condensation refrigeration system, comprising:
compressor and evaporimeter still include one-level condenser and second grade condenser, first throttling arrangement and second throttling arrangement, the one-level condenser with the exit linkage of compressor, the export of one-level condenser with the entry linkage of second grade condenser, and be in the one-level condenser with still be provided with on the pipeline between the second grade condenser first throttling arrangement, the exit linkage of second grade condenser the second throttling arrangement, second throttling arrangement's the other end is connected the evaporimeter.
Preferably, still including letting in one-level inlet tube in the one-level condenser, the one-level inlet tube let in water in the one-level condenser and with the refrigerant pipeline in the one-level condenser carries out the heat transfer, the one-level outlet pipe is connected to the exit end of one-level condenser, be provided with first control valve on the one-level inlet tube.
Preferably, the condenser also comprises a second-stage water inlet pipe which can be communicated with the second-stage condenser, the second-stage water inlet pipe is communicated with water in the second-stage condenser and exchanges heat with a refrigerant pipeline in the second-stage condenser, the outlet end of the second-stage condenser is connected with a second-stage water outlet pipe, and a second control valve is arranged on the second-stage water outlet pipe.
Preferably, when the water-saving device comprises a first-stage water inlet pipe and a second-stage water outlet pipe, the water-saving device further comprises a bypass pipe, one end of the bypass pipe is communicated with the second-stage water outlet pipe, the other end of the bypass pipe is communicated with the first-stage water inlet pipe, and the bypass pipe is further provided with a third control valve.
Preferably, when a first control valve is included, the first control valve is a solenoid valve; and/or when a second control valve is included, the second control valve is a solenoid valve; and/or when a third control valve is included, the third control valve is a solenoid valve.
Preferably, the first-stage condenser can release heat and cool in an air cooling mode, and the second-stage condenser can release heat and cool in an air cooling mode.
Preferably, the wind heated by the secondary condenser can be conducted into the primary condenser to be subjected to secondary heating.
Preferably, the compressor includes a first compression unit and a second compression unit, the refrigeration system further includes a first intermediate heat exchanger and a first branch, the first intermediate heat exchanger is arranged on a pipeline between the secondary condenser and the second throttling device, one end of the first branch is connected to a pipeline between the secondary condenser and the first intermediate heat exchanger, the other end of the first branch is communicated into the first intermediate heat exchanger, meanwhile, an outlet pipeline of the first compression unit is also communicated into the first intermediate heat exchanger, an outlet of the first intermediate heat exchanger is communicated to an inlet of the second compression unit, a pipeline between the secondary condenser and the second throttling device penetrates through the first intermediate heat exchanger and exchanges heat with a refrigerant in the first intermediate heat exchanger, and a third throttling device is further arranged on the first branch pipeline;
or the compressor comprises a first compression unit, a second compression unit and a third compression unit, the air supplementing port is positioned between the first compression unit and the second compression unit, the refrigeration system further comprises a first intermediate heat exchanger and a first branch, the first intermediate heat exchanger is arranged on a pipeline between the first-stage condenser and the first throttling device, one end of the first branch is connected to a pipeline between the first-stage condenser and the first intermediate heat exchanger, the other end of the first branch is communicated into the first intermediate heat exchanger, an outlet pipeline of the second compression unit is also communicated into the first intermediate heat exchanger, an outlet of the first intermediate heat exchanger is communicated to an inlet of the third compression unit, a pipeline between the first-stage condenser and the first throttling device penetrates through the first intermediate heat exchanger and exchanges heat with refrigerant inside the first intermediate heat exchanger, and a third throttling device is also arranged on the first branch.
Preferably, the compressor comprises a first compression unit and a second compression unit, the refrigeration system further comprises a second intermediate heat exchanger and a second branch, the second intermediate heat exchanger is arranged on a pipeline between the second-stage condenser and the second throttling device, one end of the second branch is connected to a pipeline between the second-stage condenser and the second intermediate heat exchanger, the other end of the second branch penetrates through the second intermediate heat exchanger and is communicated to a pipeline between an outlet of the first compression unit and an inlet of the second compression unit, a pipeline between the second-stage condenser and the second throttling device penetrates through the second intermediate heat exchanger and exchanges heat with the second branch inside the second intermediate heat exchanger, and a fourth throttling device is further arranged on the second branch;
or, the compressor comprises a first compression unit, a second compression unit and a third compression unit, the air supplementing port is positioned between the first compression unit and the second compression unit, the refrigeration system further comprises a second intermediate heat exchanger and a second branch, the second intermediate heat exchanger is arranged on a pipeline between the first-stage condenser and the first throttling device, one end of the second branch is connected to a pipeline between the first-stage condenser and the second intermediate heat exchanger, the other end of the second branch penetrates through the second intermediate heat exchanger and is communicated to a pipeline between an outlet of the second compression unit and an inlet of the third compression unit, a pipeline between the first-stage condenser and the first throttling device penetrates through the second intermediate heat exchanger and exchanges heat with the second branch inside the second intermediate heat exchanger, and a fourth throttling device is also arranged on the second branch.
Preferably, the compressor comprises a first compression unit and a second compression unit, the refrigeration system further comprises a third branch, one end of the third branch is connected to a pipeline between the two-stage condenser and the second throttling device, the other end of the third branch is communicated to a pipeline between an outlet of the first compression unit and an inlet of the second compression unit, and the third branch is further provided with a fifth throttling device and a fourth control valve;
or, the compressor comprises a first compression unit, a second compression unit and a third compression unit, the air supplementing port is positioned between the first compression unit and the second compression unit, the refrigeration system further comprises a third branch, one end of the third branch is connected to a pipeline between the first-stage condenser and the first throttling device, the other end of the third branch is communicated to a pipeline between an outlet of the second compression unit and an inlet of the third compression unit, and the third branch is further provided with a fifth throttling device and a fourth control valve.
Preferably, the refrigeration system further includes a heat regenerator, the heat regenerator is disposed on a pipeline between the secondary condenser and the second throttling device, the pipeline between the secondary condenser and the second throttling device penetrates through the second intermediate heat exchanger, and a pipeline between the evaporator and the inlet of the compressor also penetrates through the heat regenerator and exchanges heat with a pipe section between the secondary condenser and the second throttling device, which penetrates through the heat regenerator.
The invention also provides an air conditioner which comprises the refrigeration system.
The invention also provides a control method suitable for any one of the refrigeration systems, wherein:
when the first control valve, the second control valve and the third control valve are included at the same time: and at least one of the first control valve, the second control valve and the third control valve is selectively controlled to act according to the requirements of different hot water temperatures.
Preferably, the second control valve is arranged on the secondary water outlet pipe, and the first control valve is arranged on the primary water inlet pipe:
when water at a first temperature T1 and a second temperature T2 needs to be prepared at the same time, controlling to open the first control valve and the second control valve at the same time and close the third control valve at the same time;
when water with a first temperature T1 and a third temperature T3 needs to be prepared at the same time, controlling the second control valve and the third control valve to be opened at the same time, and closing the first control valve; wherein the second temperature T3> the second temperature T2> the first temperature T1;
when only water at a third temperature T3 needs to be produced, control opens the third control valve while closing the first and second control valves.
The refrigeration system, the air conditioner and the control method provided by the invention have the following beneficial effects:
1. the invention adopts the secondary throttling and double-condensing circulating high-low temperature system with double-condensing and intermediate throttling, compared with a primary throttling refrigeration circulating system, the invention fully utilizes the latent heat and the sensible heat of the refrigerant after primary throttling released by the secondary condenser under the condition of the same evaporation pressure, superheat degree, supercooling degree and refrigerant circulating quantity, and greatly improves the heating capacity and the heating performance coefficient of the system.
2. The condensation heat dissipation capacity of the secondary throttling double-condensation circulating high-temperature and low-temperature system is larger, so that the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with those of a primary throttling refrigerating circulating system.
3. Because the secondary throttling and double-condensing circulation high-low temperature system adopts secondary throttling, the operating environment temperature range of the secondary throttling and double-condensing circulation high-low temperature system is larger than that of the primary throttling and refrigerating circulation system, and the evaporation temperature can be lower, so that the secondary throttling and double-condensing circulation high-low temperature system is suitable for lower environment temperature to heat.
4. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.
5. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, so that the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized;
6. compared with an independent secondary throttling double-condensing circulation system, the invention further increases the supercooling degree of the refrigerant before entering the evaporator, further enhances the refrigeration performance coefficient or the heating performance coefficient, effectively reduces the temperature of the refrigerant after the primary compression unit, fully cools the refrigerant to the saturation temperature (the superheat degree is 0), can effectively reduce the exhaust superheat degree of the compressor, and effectively reduces the power consumption of the compressor;
7. compared with an independent secondary throttling double-condensing circulation system, the invention further increases the supercooling degree of the refrigerant before entering the evaporator, further enhances the refrigeration performance coefficient or the heating performance coefficient, effectively reduces the temperature of the refrigerant after the primary compression unit, cools the refrigerant (the refrigerant is not fully cooled to the saturation temperature), can effectively reduce the exhaust superheat degree of the compressor, and effectively reduces the power consumption of the compressor;
8. compared with an independent secondary throttling double-condensing circulation system, the intermediate liquid spraying system has the advantages that the temperature of the refrigerant after the primary compression unit is effectively reduced, the refrigerant is cooled (to the saturation temperature or not) to the saturation temperature, the exhaust superheat degree of the compressor can be effectively reduced, the power consumption of the compressor is effectively reduced, and the refrigeration performance coefficient or the heating performance coefficient is further enhanced;
9. compared with an independent secondary throttling double-condensing circulation system, the invention can further increase the supercooling degree of the refrigerant before entering the evaporator, further enhance the refrigeration performance coefficient or the heating performance coefficient, improve the suction superheat degree of the refrigerant before entering the air suction port of the compressor, prevent the liquid impact of the compressor and improve the reliability of the compressor.
Drawings
FIG. 1 is a schematic diagram of a secondary throttling dual condensing cycle high and low temperature system of the present invention;
FIG. 2 is a pressure-enthalpy diagram of the secondary throttling dual condensing cycle high and low temperature system of the present invention;
FIG. 3 is a comparison pressure-enthalpy diagram of the secondary throttling dual-condensing cycle high-low temperature system of the present invention and the existing primary throttling refrigeration cycle system;
FIG. 4 is a schematic diagram of a secondary throttling double condensation + full intercooling cyclic high and low temperature system of the present invention;
FIG. 5 is a pressure-enthalpy diagram of the secondary throttling double condensation plus full intercooling cyclic high and low temperature system of the present invention;
FIG. 6 is a schematic diagram of a secondary throttling double condensation and incomplete intercooling cycle high and low temperature system of the present invention;
FIG. 7 is a pressure-enthalpy diagram of the secondary throttling double condensation plus incomplete intercooling cycle high and low temperature system of the present invention;
FIG. 8 is a schematic diagram of a secondary throttling double condensation plus intermediate spray circulation high and low temperature system of the present invention;
FIG. 9 is a pressure-enthalpy diagram of the secondary throttling double condensation plus intermediate spray circulation high and low temperature system of the present invention;
FIG. 10 is a schematic diagram of a secondary throttling double condensation and regenerative cycle high and low temperature system of the present invention;
FIG. 11 is a pressure-enthalpy diagram of a secondary throttling double condensation and regenerative cycle high and low temperature system of the present invention.
The reference numerals are represented as:
1. a compressor; 101. a first compression unit; 102. a second compression unit; 2. a first-stage condenser; 3. A first throttling device; 4. a secondary condenser; 5. a second throttling device; 6. an evaporator; 7. a second-stage water inlet pipe; 8. a secondary water outlet pipe; 9. a second control valve; 10. a bypass pipe; 11. a third control valve; 12. a first-stage water inlet pipe; 13. a first control valve; 14. a primary water outlet pipe; 15. a first intermediate heat exchanger; 16. a first branch; 17. a third throttling means; 18. a second intermediate heat exchanger; 19. a second branch circuit; 20. a fourth throttling device; 21. a third branch; 22. a fifth throttling device; 23. a fourth control valve; 24. a regenerator.
Detailed Description
As shown in fig. 1-3, the present invention provides a secondary throttling dual-condensation refrigeration system, comprising:
1. The invention adopts the secondary throttling and double-condensing circulating high-low temperature system with double-condensing and intermediate throttling, compared with a primary throttling refrigeration circulating system, the invention fully utilizes the latent heat and the sensible heat of the refrigerant after primary throttling released by the secondary condenser under the condition of the same evaporation pressure, superheat degree, supercooling degree and refrigerant circulating quantity, and greatly improves the heating capacity and the heating performance coefficient of the system.
2. The condensation heat dissipation capacity of the secondary throttling double-condensation circulating high-temperature and low-temperature system is larger, so that the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with those of a primary throttling refrigerating circulating system.
3. Because the secondary throttling and double-condensing circulation high-low temperature system adopts secondary throttling, the operating environment temperature range of the secondary throttling and double-condensing circulation high-low temperature system is larger than that of the primary throttling and refrigerating circulation system, and the evaporation temperature can be lower, so that the secondary throttling and double-condensing circulation high-low temperature system is suitable for lower environment temperature to heat.
4. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.
5. Because the secondary throttling double-condensation circulating high-low temperature system adopts the double condensers, the condensing pressure of each condenser is different, the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized.
Preferably, still including letting in one-level inlet tube 12 in the one-level condenser 2, one-level inlet tube 12 let in water in the one-level condenser 2 and with the refrigerant pipeline in the one-level condenser 2 carries out the heat transfer, one-level outlet pipe 14 is connected to the exit end of one-level condenser 2 be provided with first control valve 13 on the one-level inlet tube 12. The first-stage water inlet pipe structure can effectively receive water from the outside, so that the water is heated and heated in the first-stage condenser to achieve the purpose of preparing hot water, the hot water is discharged from the first-stage water outlet pipe, and the water inlet passage of the first-stage water inlet pipe can be effectively controlled through the arrangement of the first control valve.
Preferably, the system further comprises a second-stage water inlet pipe 7 capable of being communicated with the second-stage condenser 4, the second-stage water inlet pipe 7 is used for communicating water into the second-stage condenser 4 and exchanging heat with a refrigerant pipeline in the second-stage condenser 4, the outlet end of the second-stage condenser 4 is connected with a second-stage water outlet pipe 8, and a second control valve 9 is arranged on the second-stage water outlet pipe 8. The water inlet pipe is connected with the water outlet pipe, the water inlet pipe is connected with the water inlet pipe, the water inlet pipe is connected with the water outlet pipe, the water outlet pipe is connected with the water inlet pipe, the water inlet pipe is connected with the water outlet pipe, and the water outlet pipe is connected.
Preferably, when the water heater comprises a first-stage water inlet pipe 12 and a second-stage water outlet pipe 8, the water heater further comprises a bypass pipe 10, one end of the bypass pipe 10 is communicated with the second-stage water outlet pipe 8, the other end of the bypass pipe 10 is communicated with the first-stage water inlet pipe 12, and the bypass pipe 10 is further provided with a third control valve 11. The invention is a further preferable structure form, namely, hot water in a secondary water outlet pipe (with lower temperature) can be effectively guided into a primary water inlet pipe through the arrangement of the bypass pipe, so that hot water with higher temperature is produced in the primary condenser, and the purpose of two-stage hot water production is achieved.
Preferably, when the first control valve 13 is included, the first control valve 13 is a solenoid valve; and/or when a second control valve 9 is included, the second control valve 9 is a solenoid valve; and/or when a third control valve 13 is included, the third control valve 11 is a solenoid valve. The solenoid valve is the preferred structural form of several control valves, can form more intelligent accurate control.
Preferably, the primary condenser 2 can release heat and cool in an air cooling mode, and the secondary condenser 4 can release heat and cool in an air cooling mode. The air-cooled type air conditioner is another preferable structure form of the invention, namely, the air-cooled type air conditioner is used for forming cooling of the secondary condenser, effectively raising the temperature of the air, forming hot air, heating a room, drying and the like.
Preferably, the first and second electrodes are formed of a metal,
the wind heated by the secondary condenser 4 can be conducted into the primary condenser 2 to be heated secondarily. Through the structure, air can be effectively accessed from the outside, so that the air is heated and warmed in the secondary condenser, the purpose of preparing hot air (different from the hot air temperature of the primary condenser, lower secondary condensation pressure and slightly lower temperature) is achieved, the purpose of heating the air step by step is achieved, and the requirements of environments with air (hot air) at different temperatures are met.
As shown in fig. 4 to 5, preferably, the compressor 1 comprises a first compression unit 101 and a second compression unit 102, the refrigeration system further comprises a first intermediate heat exchanger 15 and a first branch 16, the first intermediate heat exchanger 15 is arranged on the pipeline between the two-stage condenser 4 and the second throttling device 5, one end of the first branch 16 is connected to the pipeline between the two-stage condenser 4 and the first intermediate heat exchanger 15, the other end of the first branch opens into the first intermediate heat exchanger 15, the outlet pipeline of the first compression unit 101 also opens into the first intermediate heat exchanger 15, the outlet of the first intermediate heat exchanger 15 opens into the inlet of the second compression unit 102, the pipeline between the two-stage condenser 4 and the second throttling device extends through the first intermediate heat exchanger 15 and exchanges heat with the refrigerant inside the first intermediate heat exchanger 15, a third throttling device 17 is further arranged on the first branch 16;
alternatively, the compressor 1 comprises a first compression unit 101, a second compression unit 102 and a third compression unit 103, the air supplement port is positioned between the first compression unit 101 and the second compression unit 102, the refrigeration system further comprises a first intermediate heat exchanger 15 and a first branch 16, the first intermediate heat exchanger 15 is arranged on the pipeline between the first-stage condenser 2 and the first throttling device 3, one end of the first branch 16 is connected to the pipeline between the first-stage condenser 2 and the first intermediate heat exchanger 15, the other end of the first branch leads into the first intermediate heat exchanger 15, meanwhile, the outlet pipeline of the second compression unit 101 also leads into the first intermediate heat exchanger 15, the outlet of the first intermediate heat exchanger 15 leads to the inlet of the third compression unit 103, and the pipeline between the first-stage condenser 2 and the first throttling device 3 penetrates through the first intermediate heat exchanger 15, And exchanges heat with the refrigerant inside the first intermediate heat exchanger 15, and a third throttling device 17 is further provided on the first branch line 16.
Compared with an independent secondary throttling double-condensing circulation system, the invention further increases the supercooling degree of the refrigerant before entering the evaporator, further enhances the refrigeration performance coefficient or the heating performance coefficient, effectively reduces the temperature of the refrigerant after the primary compression unit, fully cools the refrigerant to the saturation temperature (the superheat degree is 0), can effectively reduce the exhaust superheat degree of the compressor, and effectively reduces the power consumption of the compressor.
As shown in fig. 6 to 7, preferably, the compressor 1 includes a first compression unit 101 and a second compression unit 102, the refrigeration system also comprises a second intermediate heat exchanger 18 and a second branch 19, the second intermediate heat exchanger 18 being arranged on the line between the secondary condenser 4 and the second throttling device 5, one end of the second branch 19 is connected to a pipeline between the secondary condenser 4 and the second intermediate heat exchanger 18, the other end penetrates through the second intermediate heat exchanger 18 and is communicated to a pipeline between an outlet of the first compression unit 101 and an inlet of the second compression unit 102, a pipeline between the secondary condenser 4 and the second throttling device 5 penetrates through the second intermediate heat exchanger 18 and exchanges heat with the second branch 19 in the second intermediate heat exchanger 18, and a fourth throttling device 20 is further arranged on the second branch 19;
alternatively, the compressor 1 comprises a first compression unit 101, a second compression unit 102 and a third compression unit 103, the air supplement port is located between the first compression unit 101 and the second compression unit 102, the refrigeration system further comprises a second intermediate heat exchanger 18 and a second branch 19, the second intermediate heat exchanger 18 is arranged on the pipeline between the first-stage condenser 2 and the first throttling device 3, one end of the second branch 19 is connected to the pipeline between the first-stage condenser 2 and the second intermediate heat exchanger 18, the other end of the second branch 19 penetrates through the second intermediate heat exchanger 18 and is communicated to the pipeline between the outlet of the second compression unit 102 and the inlet of the third compression unit 103, the pipeline between the first-stage condenser 2 and the first throttling device 3 penetrates through the second intermediate heat exchanger 18 and exchanges heat with the second branch 19 inside the second intermediate heat exchanger 18, and a fourth throttling device 20 is also arranged on the second branch 19.
Compared with an independent secondary throttling double-condensing circulation system, the invention further increases the supercooling degree of the refrigerant before entering the evaporator, further enhances the refrigeration performance coefficient or the heating performance coefficient, effectively reduces the temperature of the refrigerant after the primary compression unit, cools the refrigerant (the refrigerant is not fully cooled to the saturation temperature), can effectively reduce the exhaust superheat degree of the compressor, and effectively reduces the power consumption of the compressor.
As shown in fig. 8-9, preferably, the compressor 1 includes a first compression unit 101 and a second compression unit 102, the refrigeration system further includes a third branch 21, one end of the third branch 21 is connected to a pipeline between the two-stage condenser 4 and the second throttling device 5, and the other end is connected to a pipeline between an outlet of the first compression unit 101 and an inlet of the second compression unit 102, and a fifth throttling device 22 and a fourth control valve 23 are further disposed on the third branch 21;
or, the compressor 1 includes a first compression unit 101, a second compression unit 102 and a third compression unit 103, the refrigeration system further includes a third branch 21, one end of the third branch 21 is connected to a pipeline between the first-stage condenser 2 and the first throttling device 3, and the other end is connected to a pipeline between an outlet of the second compression unit 102 and an inlet of the third compression unit 103, and the third branch 21 is further provided with a fifth throttling device 22 and a fourth control valve 23.
Compared with a single secondary throttling double-condensing circulation system, the intermediate liquid spraying system has the advantages that the temperature of the refrigerant after the primary compression unit is effectively reduced, the refrigerant is cooled (to the saturation temperature or not) to the saturation temperature, the exhaust superheat degree of the compressor can be effectively reduced, the power consumption of the compressor is effectively reduced, and the refrigeration performance coefficient or the heating performance coefficient is further enhanced.
As shown in fig. 10 to 11, preferably, the refrigeration system further includes a heat regenerator 24, the heat regenerator 24 is disposed on a pipeline between the secondary condenser 4 and the second throttling device 5, the pipeline between the secondary condenser 4 and the second throttling device 5 extends through the second intermediate heat exchanger 18, and a pipeline between the evaporator 6 and the inlet of the compressor 1 also extends through the heat regenerator 24 and exchanges heat with a pipe section between the secondary condenser 4 and the second throttling device 5 extending through the heat regenerator 24.
Compared with an independent secondary throttling double-condensing circulation system, the invention can further increase the supercooling degree of the refrigerant before entering the evaporator, further enhance the refrigeration performance coefficient or the heating performance coefficient, improve the suction superheat degree of the refrigerant before entering the air suction port of the compressor, prevent the liquid impact of the compressor and improve the reliability of the compressor.
The invention also provides an air conditioner which comprises the secondary throttling double-condensation refrigeration system.
The invention also provides a control method suitable for any one of the secondary throttling double-condensation refrigeration systems, wherein the control method comprises the following steps:
when the first control valve, the second control valve and the third control valve are included at the same time: and at least one of the first control valve, the second control valve and the third control valve is selectively controlled to act according to the requirements of different hot water temperatures.
1. The invention adopts the secondary throttling and double-condensing circulating high-low temperature system with double-condensing and intermediate throttling, compared with a primary throttling refrigeration circulating system, the invention fully utilizes the latent heat and the sensible heat of the refrigerant after primary throttling released by the secondary condenser under the condition of the same evaporation pressure, superheat degree, supercooling degree and refrigerant circulating quantity, and greatly improves the heating capacity and the heating performance coefficient of the system.
2. The condensation heat dissipation capacity of the secondary throttling double-condensation circulating high-temperature and low-temperature system is larger, so that the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with those of a primary throttling refrigerating circulating system.
3. Because the secondary throttling and double-condensing circulation high-low temperature system adopts secondary throttling, the operating environment temperature range of the secondary throttling and double-condensing circulation high-low temperature system is larger than that of the primary throttling and refrigerating circulation system, and the evaporation temperature can be lower, so that the secondary throttling and double-condensing circulation high-low temperature system is suitable for lower environment temperature to heat.
4. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.
5. Because the secondary throttling double-condensation circulating high-low temperature system adopts the double condensers, the condensing pressure of each condenser is different, the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized.
Preferably, the second control valve 9 is arranged on the secondary water outlet pipe 8, and the first control valve 13 is arranged on the primary water inlet pipe 12:
when water at a first temperature T1 and a second temperature T2 needs to be prepared at the same time, the first control valve 13 and the second control valve 9 are selected to be opened at the same time, and the third control valve 11 is closed at the same time;
when water with the first temperature T1 and the third temperature T3 needs to be prepared at the same time, the second control valve 9 and the third control valve 11 are selected to be opened at the same time, and the first control valve 13 is closed; wherein the second temperature T3> the second temperature T2> the first temperature T1;
when it is only necessary to make water at a third temperature T3, the third control valve 11 is selectively opened while the first control valve 13 and the second control valve 9 are closed.
The secondary throttling double-condensation circulation high-low temperature system is explained by combining the attached drawings 1-3 as follows:
referring to the attached figure 1, a schematic diagram of a secondary throttling double-condensation cycle high-low temperature system and a pressure-enthalpy diagram of a secondary throttling double-condensation cycle high-low temperature system are shown in the attached figure 2, a compressor sucks low-temperature superheated refrigerant b from an evaporator for compression, and compressed high-temperature high-pressure superheated refrigerant c is discharged into a primary condenser and condensed by cooling water into high-temperature high-pressure wet vapor refrigerant d; the high-temperature high-pressure wet vapor refrigerant d after primary condensation is throttled by a first throttling device to become a medium-temperature medium-pressure wet vapor refrigerant e; the medium-temperature medium-pressure wet vapor refrigerant e after primary throttling enters a secondary condenser and is condensed to medium-temperature medium-pressure supercooling refrigerant g by cooling water; the medium-temperature medium-pressure subcooled refrigerant g after secondary condensation is throttled by a second throttling device to form a low-temperature low-pressure wet vapor refrigerant h; the low-temperature low-pressure wet vapor refrigerant h after secondary throttling enters the evaporator to absorb heat to a low-temperature superheated refrigerant state b, so that a secondary throttling double-condensation cycle is completed.
Because two low temperature systems of two condensation circulations of secondary throttle have two condensers, the condensing pressure of each condenser is different, so the cooling method of condenser is various for the business turn over temperature of every condenser can freely be controlled and adjusted, can realize the multi-functional operating mode of different temperature water uses.
The first cooling method is to open the first control valve and open the second control valve simultaneously, and close the third control valve 11 simultaneously. The water inlet source temperature of the first-stage water inlet pipe and the water inlet source temperature of the second-stage water inlet pipe can be different, and the condensation temperature of the second-stage condenser is lower than that of the first-stage condenser, so that the water outlet temperature of the second-stage water outlet pipe is generally lower than that of the first-stage water outlet pipe, and therefore multifunctional working conditions that hot water at the first temperature T1 and the second temperature T2 is prepared to be used are achieved.
In the second cooling method, the second control valve and the third control valve are opened at the same time, and the first control valve is closed. The cooling water enters from the secondary water inlet pipe, after the cooling water is heated by the refrigerant of the secondary condenser, one part of the heated cooling water flows out from the secondary water outlet pipe for users to use, the other part of the heated cooling water enters into the primary condenser and is continuously heated by the refrigerant of the primary condenser, and the heated high-temperature hot water flows out from the primary water outlet pipe for users to use, so that the multifunctional working condition that the hot water with the first temperature T1 and the third temperature T3 is prepared for use is realized.
The third cooling mode is to open the third control valve and close the first control valve and the second control valve at the same time. And cooling water enters from the secondary water inlet pipe, and is heated into high-temperature hot water by the refrigerant of the secondary condenser and the refrigerant of the primary condenser, so that the high-flow requirement of the hot water at the third temperature T3 can be realized.
Referring to fig. 3, a pressure-enthalpy diagram of the secondary throttling double-condensation cycle high-low temperature system is compared with a pressure-enthalpy diagram of a conventional primary throttling refrigeration cycle system, and under the condition of the same evaporation pressure, superheat degree and refrigerant circulation volume, the condensation pressure of the primary throttling refrigeration cycle system is in the middle of two condensation pressures of the secondary throttling double-condensation cycle system. Compared with a primary throttling refrigeration cycle system, the compression power consumption of the secondary throttling double-condensation cycle system is increased by W ═ hc-hhThe secondary throttling double-condensation circulating high-low temperature system fully utilizes the latent heat and sensible heat of the refrigerant released by the secondary condenser after the primary throttling, and has more heating capacity than the primary throttling refrigeration circulating system by Qh＝hi-hfRefrigeration capacity is much Qc＝hj-hg. Compared with a primary throttling refrigeration cycle system, the secondary throttling double-condensation cycle system has the advantages that the amplification degree of the heating capacity and the refrigerating capacity is far greater than that of the compression power consumption, so that the secondary throttling double-condensation cycle high-low temperature system has higher heating capacity, refrigerating capacity, heating performance coefficient and refrigerating performance coefficient.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (14)
1. The utility model provides a two condensing refrigerating system of secondary throttle which characterized in that: the method comprises the following steps:
compressor (1) and evaporimeter (6), still include one-level condenser (2) and second grade condenser (4), first throttling arrangement (3) and second throttling arrangement (5), one-level condenser (2) with the exit linkage of compressor (1), the export of one-level condenser (2) with the entry linkage of second grade condenser (4) and be in one-level condenser (2) with still be provided with on the pipeline between second grade condenser (4) first throttling arrangement (3), the exit linkage of second grade condenser (4) second throttling arrangement (5), the other end of second throttling arrangement (5) is connected evaporimeter (6).
2. The secondary throttle dual-condensation refrigeration system according to claim 1, characterized in that:
still including letting in one-level inlet tube (12) in one-level condenser (2), one-level inlet tube (12) let in water in one-level condenser (2) and with the refrigerant pipeline in one-level condenser (2) carries out the heat transfer, one-level outlet pipe (14) is connected to the exit end of one-level condenser (2), be provided with first control valve (13) on one-level inlet tube (12).
3. The double-throttling double-condensing refrigeration system according to any one of claims 1-2, characterized in that:
still including letting in second grade inlet tube (7) in second grade condenser (4), second grade inlet tube (7) let in water in second grade condenser (4) and with the refrigerant pipeline in second grade condenser (4) carries out the heat transfer, second grade outlet pipe (8) are connected to the exit end of second grade condenser (4) be provided with second control valve (9) on second grade outlet pipe (8).
4. The secondary throttling dual condensation refrigeration system of claim 3, wherein:
when the water purifier comprises a primary water inlet pipe (12) and a secondary water outlet pipe (8), the water purifier further comprises a bypass pipe (10), one end of the bypass pipe (10) is communicated with the secondary water outlet pipe (8), the other end of the bypass pipe is communicated with the primary water inlet pipe (12), and a third control valve (11) is further arranged on the bypass pipe (10).
5. The secondary throttle dual-condensation refrigeration system according to claim 4, characterized in that:
when a first control valve (13) is included, the first control valve (13) is an electromagnetic valve; and/or when a second control valve (9) is included, the second control valve (9) is a solenoid valve; and/or when a third control valve (13) is included, the third control valve (11) is a solenoid valve.
6. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 5, characterized in that:
the primary condenser (2) can release heat and cool in an air cooling mode, and the secondary condenser (4) can release heat and cool in an air cooling mode.
7. The secondary throttle dual-condensation refrigeration system according to claim 6, characterized in that:
the air heated by the secondary condenser (4) can be conducted into the primary condenser (2) to be heated secondarily.
8. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 7, characterized in that:
the compressor (1) comprises a first compression unit (101) and a second compression unit (102), the refrigeration system further comprises a first intermediate heat exchanger (15) and a first branch (16), the first intermediate heat exchanger (15) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), one end of the first branch (16) is connected to a pipeline between the secondary condenser (4) and the first intermediate heat exchanger (15), the other end of the first branch is communicated into the first intermediate heat exchanger (15), an outlet pipeline of the first compression unit (101) is communicated into the first intermediate heat exchanger (15), an outlet of the first intermediate heat exchanger (15) is communicated to an inlet of the second compression unit (102), and a pipeline between the secondary condenser (4) and the second throttling device penetrates through the first intermediate heat exchanger (15), The heat exchange is carried out between the refrigerant and the refrigerant in the first intermediate heat exchanger (15), and a third throttling device (17) is further arranged on the first branch (16);
or, the compressor (1) comprises a first compression unit (101), a second compression unit (102) and a third compression unit (103), the refrigeration system further comprises a first intermediate heat exchanger (15) and a first branch (16), the first intermediate heat exchanger (15) is arranged on a pipeline between the first-stage condenser (2) and the first throttling device (3), one end of the first branch (16) is connected to a pipeline between the first-stage condenser (2) and the first intermediate heat exchanger (15), the other end of the first branch leads into the first intermediate heat exchanger (15), an outlet pipeline of the second compression unit (101) is communicated to the first intermediate heat exchanger (15), an outlet of the first intermediate heat exchanger (15) is communicated to an inlet of the third compression unit (103), and a pipeline between the first-stage condenser (2) and the first throttling device (3) penetrates through the first intermediate heat exchanger (15), And exchanges heat with the refrigerant in the first intermediate heat exchanger (15), and a third throttling device (17) is arranged on the first branch (16).
9. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 8, characterized in that:
the compressor (1) comprises a first compression unit (101) and a second compression unit (102), the refrigeration system further comprises a second intermediate heat exchanger (18) and a second branch (19), the second intermediate heat exchanger (18) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), one end of the second branch (19) is connected to a pipeline between the secondary condenser (4) and the second intermediate heat exchanger (18), the other end of the second branch penetrates through the second intermediate heat exchanger (18) and is communicated to a pipeline between an outlet of the first compression unit (101) and an inlet of the second compression unit (102), a pipeline between the secondary condenser (4) and the second throttling device (5) penetrates through the second intermediate heat exchanger (18) and exchanges heat with the second branch (19) inside the second intermediate heat exchanger (18), a fourth throttling device (20) is further arranged on the second branch (19);
or, the compressor (1) comprises a first compression unit (101), a second compression unit (102) and a third compression unit (103), the refrigeration system further comprises a second intermediate heat exchanger (18) and a second branch (19), the second intermediate heat exchanger (18) is arranged on a pipeline between the first-stage condenser (2) and the first throttling device (3), one end of the second branch (19) is connected to a pipeline between the first-stage condenser (2) and the second intermediate heat exchanger (18), the other end of the second branch penetrates through the second intermediate heat exchanger (18) and is communicated to a pipeline between an outlet of the second compression unit (102) and an inlet of the third compression unit (103), and a pipeline between the first-stage condenser (2) and the first throttling device (3) penetrates through the second intermediate heat exchanger (18), And exchanges heat with the second branch (19) in the second intermediate heat exchanger (18), and a fourth throttling device (20) is further arranged on the second branch (19).
10. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 9, characterized in that:
the compressor (1) comprises a first compression unit (101) and a second compression unit (102), the refrigeration system further comprises a third branch (21), one end of the third branch (21) is connected to a pipeline between the two-stage condenser (4) and the second throttling device (5), the other end of the third branch is communicated to a pipeline between an outlet of the first compression unit (101) and an inlet of the second compression unit (102), and a fifth throttling device (22) and a fourth control valve (23) are further arranged on the third branch (21);
or, the compressor (1) comprises a first compression unit (101), a second compression unit (102) and a third compression unit (103), the refrigeration system further comprises a third branch (21), one end of the third branch (21) is connected to a pipeline between the first-stage condenser (2) and the first throttling device (3), the other end of the third branch is communicated to a pipeline between an outlet of the second compression unit (102) and an inlet of the third compression unit (103), and a fifth throttling device (22) and a fourth control valve (23) are further arranged on the third branch (21).
11. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 10, characterized in that:
the refrigerating system further comprises a heat regenerator (24), the heat regenerator (24) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), the pipeline between the secondary condenser (4) and the second throttling device (5) penetrates through the heat regenerator (24), and a pipeline between the evaporator (6) and an inlet of the compressor (1) also penetrates through the heat regenerator (24) and exchanges heat with a pipeline between the secondary condenser (4) and the second throttling device (5) and penetrates through the heat regenerator (24).
12. An air conditioner, characterized in that:
comprising the double-throttling double-condensing refrigeration system of any of claims 1 to 11.
13. A control method suitable for use in a double throttling double condensing refrigeration system according to any one of claims 1 to 11, characterized by:
when the first control valve, the second control valve and the third control valve are included at the same time: and at least one of the first control valve, the second control valve and the third control valve is selectively controlled to act according to the requirements of different hot water temperatures.
14. The control method according to claim 13, characterized in that:
the second control valve (9) is arranged on the secondary water outlet pipe (8), and the first control valve (13) is arranged on the primary water inlet pipe (12):
when it is desired to make water at a first temperature T1 and a second temperature T2 simultaneously, the simultaneous opening of the first control valve (13) and the second control valve (9) and the simultaneous closing of the third control valve (11) are selected;
when water with a first temperature T1 and a third temperature T3 needs to be prepared at the same time, the second control valve (9) and the third control valve (11) are selectively opened at the same time, and the first control valve (13) is closed; wherein the second temperature T3> the second temperature T2> the first temperature T1;
when it is only necessary to make water at a third temperature T3, the third control valve (11) is selectively opened, while the first control valve (13) and the second control valve (9) are closed.
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