CN107024031B - Three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference - Google Patents
Three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference Download PDFInfo
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion 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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
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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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/004—Gas cycle refrigeration machines using a compressor of the rotary type
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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
- F25B2347/00—Details for preventing or removing deposits or corrosion
- F25B2347/02—Details of defrosting cycles
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the 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
- F25B2500/00—Problems to be solved
- F25B2500/29—High ambient temperatures
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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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Abstract
The invention relates to the technical field of air-conditioning heat pumps, in particular to a three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference. The system comprises a main path compressor, a main path oil separator, a four-way reversing valve, an outdoor side heat exchanger, an outdoor side fan, a first one-way valve, a second one-way valve, a third one-way valve, a fourth one-way valve, a fifth one-way valve, a sixth one-way valve, a recooler, a drying filter, an observation mirror, a first expansion valve, a middle pressure gas-liquid separator, a second expansion valve, an indoor side heat exchanger, a low pressure gas-liquid separator, an evaporation pressure regulator, an auxiliary path compressor, an auxiliary path oil separator and a connecting pipeline; the outstanding problems of a summer high-temperature refrigeration working mode and a winter low-temperature heating working mode are solved; meanwhile, the energy-saving defrosting device has the characteristics of wide energy adjusting range, quick defrosting, energy conservation and the like, and widens the application field of the air-cooled heat pump.
Description
Technical Field
The invention relates to the technical field of air-conditioning heat pumps, in particular to a three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference.
Background
In the face of the increasingly prominent problems of energy shortage and environmental pollution, the development of an air-conditioning heat pump device which is efficient, energy-saving, good in comfort, safe and reliable becomes the key of sustainable and rapid development of the air-conditioning industry. The conventional air source heat pump device takes air as a cold and heat source, has simple structure and convenient installation and use, can fully utilize energy in the air, and is high-efficiency and energy-saving air conditioning equipment. However, when outdoor temperature is too high in summer, the condensing pressure of the air source heat pump device is too high, the compression ratio of the compressor is too large, the exhaust temperature is too high, the refrigerating capacity and the energy efficiency ratio of the air source heat pump device are rapidly reduced, and even the compressor can be frequently and protectively shut down; similarly, when the outdoor air temperature is too low in winter, the evaporation temperature of the air source heat pump device is too low, the surface of an evaporator is frosted seriously, the compression ratio of a compressor is too large, the exhaust temperature is too high, the heating capacity and the energy efficiency ratio of the air source heat pump device are reduced sharply, and if the traditional reverse defrosting mode is adopted, the air source heat pump device has the defects of long defrosting time, poor effect and the like, and even the device can not run normally. In conclusion, when the outdoor temperature is too high or too low, the conventional air source heat pump has the above outstanding problems, and the popularization and application of the air source heat pump are seriously influenced.
In view of the shortcomings of the conventional air source heat pump device, there are three common solutions: one method adopts a traditional auxiliary electric heater mode, but has lower efficiency and higher operation cost and is almost eliminated. In addition, two schemes respectively adopt a two-stage compression type refrigeration/heating circulation mode and a cascade type refrigeration/heating circulation mode, so that the problems of overlarge compression ratio and overhigh exhaust temperature of a compressor when air source heat pump is used for refrigeration under a high-temperature working condition or heating under a low-temperature working condition are solved to a certain extent, the refrigeration capacity or the heating capacity and the energy efficiency ratio of a unit are improved, but the two schemes also have the following problems: firstly, the flowing direction of a refrigerant can not be switched in winter and summer generally, and only the refrigeration performance in a single high-temperature refrigeration working mode or the heating performance in a single low-temperature heating working mode can be solved, but the system performance in two working modes of an air source heat pump in winter and summer can not be solved; secondly, when the two-stage compression cycle and the cascade cycle change along with the load of a user, the energy adjusting range is smaller, when the load is reduced, the reduction amount of energy consumption in the system energy adjusting process is smaller, and the energy efficiency ratio of the system is obviously reduced; finally, when severe frosting occurs on the surface of the evaporator of the two-stage compression cycle and the cascade cycle, how to efficiently defrost becomes a problem to be solved urgently.
Disclosure of Invention
The invention aims to provide a three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference, and aims to solve the outstanding technical problems that the compression ratio of a compressor is too large, the exhaust temperature is too high, the refrigerating capacity/heating capacity and the energy efficiency ratio of a system are sharply reduced and the like when the existing air source heat pump is used for refrigerating under a high-temperature working condition and heating under a low-temperature working condition.
In order to solve the technical problems, the invention adopts the following technical scheme:
a three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference comprises a main path compressor, a main path oil separator, a four-way reversing valve, an outdoor side heat exchanger, an outdoor side fan, a first one-way valve, a second one-way valve, a third one-way valve, a fourth one-way valve, a fifth one-way valve, a sixth one-way valve, a recooler, a drying filter, an observation mirror, a first expansion valve, a middle pressure gas-liquid separator, a second expansion valve, an indoor side heat exchanger, a low pressure gas-liquid separator, an evaporation pressure regulator, an auxiliary path compressor, an auxiliary path oil separator and a connecting pipeline; an exhaust port of the main path compressor is connected with an inlet of a fifth one-way valve through a main path oil separator, an outlet of the fifth one-way valve and an outlet of a sixth one-way valve are connected with a four-way reversing valve after being converged through a pipeline, the four-way reversing valve is respectively connected with interfaces of an outdoor side heat exchanger, an indoor side heat exchanger and a low-pressure gas-liquid separator through connecting pipelines, the other interface of the low-pressure gas-liquid separator is connected with an air suction port of the main path compressor, the other interface of the outdoor side heat exchanger is connected with an inlet of a first one-way valve and an outlet of a second one-way valve, an outlet of the first one-way valve is converged with an outlet of a fourth one-way valve and then connected with a main path inlet of a recooler, a main path outlet of the recooler is connected with an inlet of the medium-pressure gas-liquid separator, and a drying filter, an observation mirror and a first expansion valve are sequentially arranged on the connecting pipeline between the main path outlet of the recooler and the medium-pressure gas-liquid separator; two outlets of the medium-pressure gas-liquid separator are respectively connected with an inlet of a secondary circuit of the recooler and an inlet of the second expansion valve; the outlet of the second expansion valve is connected with the inlet of the second one-way valve and the inlet of the third one-way valve, a connecting pipeline between the outlet of the second expansion valve and the inlet of the third one-way valve and the inlet of the fourth one-way valve forms a T-shaped three-way pipeline, and the outlet of the third one-way valve and the inlet of the fourth one-way valve are converged by the connecting pipeline and then connected with the other interface of the indoor side heat exchanger; an auxiliary outlet of the recooler is connected with an air suction port of an auxiliary compressor after passing through the evaporation pressure regulator, and an exhaust port of the auxiliary compressor is connected with an inlet of a sixth one-way valve after passing through an auxiliary oil separator; all the parts are connected through connecting pipelines.
The main road compressor and the auxiliary road compressor are in any one form of a fixed-frequency scroll compressor, a fixed-frequency rolling rotor compressor, a variable-frequency scroll compressor and a variable-frequency rolling rotor compressor. The indoor side heat exchanger is in any structural form of an air-cooled heat exchanger and a water-cooled heat exchanger. The outdoor heat exchanger is any one of a finned tube heat exchanger, a stacked heat exchanger and a parallel flow heat exchanger. The outdoor fan is any one of a variable frequency fan, a fixed frequency fan and a gear shifting fan. The first expansion valve and the second expansion valve are in the form of any one of a manual expansion valve, a choke type expansion valve, a floating ball type expansion valve, a thermostatic expansion valve and an electronic expansion valve. The evaporation pressure regulator is in the form of any one of a proportional regulator, a proportional-integral regulator, a proportional-derivative regulator and a proportional-integral-derivative regulator which are controlled by the pressure before the valve (i.e. evaporation pressure). The recooler is in any structural form of a plate heat exchanger, a double-pipe heat exchanger and a flash tank.
The invention has the following beneficial effects:
the invention provides a three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference, which has novel conception and skillful unit design optimization and has the following main advantages:
(1) through the ingenious switching combination of the four-way reversing valve and the six one-way valves, the air-cooled heat pump unit can solve the outstanding problems of overhigh condensation pressure, overlarge compression ratio of a compressor, overhigh exhaust temperature and sharp reduction of the refrigerating capacity and the energy efficiency ratio in a high-temperature refrigerating working mode in summer, and can also solve the outstanding problems of overlow evaporation temperature, serious surface frosting of an evaporator, overlarge compression ratio of the compressor, overhigh exhaust temperature and sharp reduction of the heating capacity and the energy efficiency ratio in a low-temperature heating working mode in winter, thereby widening the application field of the air-cooled heat pump.
(2) Through the auxiliary regulation of the auxiliary compressor and the evaporation pressure regulator, the refrigerating capacity or the heating capacity of the air-cooled heat pump unit can be rapidly changed along with the change of user load, the energy regulation range is wide, meanwhile, high-efficiency and rapid defrosting can be realized, and the reliability, the stability and the economical efficiency of the annual operation of the air-cooled heat pump are improved.
The three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference can be widely applied to all places which can adopt air source heat pumps, such as civil buildings, public buildings, villa buildings and the like.
Drawings
Fig. 1 is a schematic diagram of the structure of the present invention.
Fig. 2 is a flow chart of a single-stage compression refrigeration mode of operation.
Fig. 3 is a flow chart of a three-pressure cooling mode of operation.
Fig. 4 is a flow chart of a single-stage compression heating operation mode.
Fig. 5 is a flow chart of a three-pressure heating operation mode.
Fig. 6 is a flow chart of an indoor cold-feeling-free fast defrosting operation mode.
FIG. 7 is a flow chart of a three-pressure fast defrosting mode of operation.
Number in the figure: 1 is a main path compressor, 2 is a main path oil separator, 3 is a four-way reversing valve, 4-1 is an outdoor side heat exchanger, 4-2 is an outdoor side fan, 5-1 is a first one-way valve, 5-2 is a second one-way valve, 5-3 is a third one-way valve, 5-4 is a fourth one-way valve, 5-5 is a fifth one-way valve, 5-6 is a sixth one-way valve, 6 is a recooler, 7 is a drying filter, 8 is an observation mirror, 9 is a first expansion valve, 10 is a medium pressure gas-liquid separator, 11 is a second expansion valve, 12 is an indoor side heat exchanger, 13 is a low pressure gas-liquid separator, 14 is an evaporation pressure regulator, 15 is an auxiliary path compressor, and 16 is an auxiliary path oil separator.
Detailed Description
The invention will be further described with reference to the following examples (figures) without restricting the invention thereto.
Example 1
As shown in FIG. 1, the invention provides a three-pressure high-efficiency air-cooled heat pump unit suitable for large temperature difference, which is characterized in that: the device comprises a main path compressor 1, a main path oil separator 2, a four-way reversing valve 3, an outdoor heat exchanger 4-1, an outdoor fan 4-2, a first one-way valve 5-1, a second one-way valve 5-2, a third one-way valve 5-3, a fourth one-way valve 5-4, a fifth one-way valve 5-5, a sixth one-way valve 5-6, a recooler 6, a drying filter 7, an observation mirror 8, a first expansion valve 9, a middle pressure gas-liquid separator 10, a second expansion valve 11, an indoor heat exchanger 12, a low pressure gas-liquid separator 13, an evaporation pressure regulator 14, an auxiliary path compressor 15, an auxiliary path oil separator 16 and a connecting pipeline. The exhaust port of the main path compressor 1 is connected with the inlet of a fifth one-way valve 5-5 through a main path oil separator 2, the outlet of the fifth one-way valve 5-5 is connected with the outlet of a sixth one-way valve 5-6, and the mixed gas outlet of the fifth one-way valve 5-5 and the sixth one-way valve is respectively connected with the corresponding interfaces of an outdoor heat exchanger 4-1, an indoor heat exchanger 12 and a low-pressure gas-liquid separator 13 through a four-way reversing valve 3 and corresponding connecting pipelines; the other interface of the low-pressure gas-liquid separator 13 is connected with the air suction port of the main-path compressor 1; the other interface of the outdoor heat exchanger 4-1 is connected with an inlet of a first one-way valve 5-1 and an outlet of a second one-way valve 5-2, an outlet of the first one-way valve 5-1 is connected with an outlet of a fourth one-way valve 5-4 and a main path inlet of a recooler 6, and a main path outlet of the recooler 6 is connected with an inlet of a medium-pressure gas-liquid separator 10 through a drying filter 7, an observation mirror 8 and a first expansion valve 9; two outlets of the medium-pressure gas-liquid separator 10 are respectively connected with an inlet of a secondary circuit of the recooler 6 and an inlet of a second expansion valve 11; an outlet of the second expansion valve 11 is connected with an inlet of a second one-way valve 5-2 and an inlet of a third one-way valve 5-3, and an outlet of the third one-way valve 5-3 and an inlet of a fourth one-way valve 5-4 are connected with the other interface of the indoor side heat exchanger 12; the bypass outlet of the recooler 6 is connected to the suction port of a bypass compressor 15 through an evaporating pressure regulator 14, and the exhaust port of the bypass compressor 15 is connected to the inlet of the sixth check valve 5-6 through a bypass oil separator 16.
The main compressor 1 and the auxiliary compressor 15 are fixed-frequency scroll compressors; the indoor side heat exchanger 12 is an air-cooled heat exchanger; the outdoor heat exchanger 4-1 is a finned tube heat exchanger; the outdoor fan 4-2 is any one of a variable frequency fan, a fixed frequency fan and a gear shifting fan. The first expansion valve 9 and the second expansion valve 11 are in the form of any one of a manual expansion valve, a choke expansion valve, a floating ball type expansion valve, a thermostatic expansion valve and an electronic expansion valve. The evaporating pressure regulator 14 is in the form of any one of a proportional regulator, a proportional-integral regulator, a proportional-derivative regulator, and a proportional-integral-derivative regulator, which are controlled by the pressure before the valve (i.e., the evaporating pressure). The recooler 6 is in any structural form of a plate heat exchanger, a double-pipe heat exchanger and a flash tank. The other structure is the same as embodiment 1.
Example 2
The main compressor 1 is a fixed-frequency scroll compressor, and the auxiliary compressor 15 is a fixed-frequency rolling rotor compressor; the indoor side heat exchanger 12 is an air-cooled heat exchanger; the outdoor heat exchanger 4-1 is a finned tube heat exchanger; the outdoor fan 4-2 is a variable frequency fan; the first expansion valve 9 is a manual expansion valve, and the second expansion valve 11 is a choke type expansion valve; the evaporating pressure regulator 14 is a proportional regulator controlled by the pressure before the valve (i.e., evaporating pressure); the subcooler 6 is a plate heat exchanger. The other structure is the same as embodiment 1.
Example 3
The main compressor 1 is a fixed-frequency rolling rotor compressor, and the auxiliary compressor 15 is a fixed-frequency scroll compressor; the indoor side heat exchanger 12 is an air-cooled heat exchanger; the outdoor heat exchanger 4-1 is a stacked heat exchanger; the outdoor fan 4-2 is a variable frequency fan; the first expansion valve 9 is a floating ball type expansion valve, and the second expansion valve 11 is a choking type expansion valve; the evaporating pressure regulator 14 is a proportional-integral regulator controlled by the pressure before the valve (i.e., evaporating pressure); the subcooler 6 is a double pipe heat exchanger. The other structure is the same as embodiment 1.
Example 4
The main compressor 1 and the auxiliary compressor 15 are frequency conversion scroll compressors; the indoor side heat exchanger 12 is a water-cooled heat exchanger; the outdoor heat exchanger 4-1 is a stacked heat exchanger; the outdoor fan 4-2 is a gear shifting fan; the first expansion valve 9 is a thermostatic expansion valve, and the second expansion valve 11 is an electronic expansion valve; the evaporating pressure regulator 14 is a proportional-differential regulator controlled by the pressure before the valve (i.e., evaporating pressure); the subcooler 6 is a plate heat exchanger. The other structure is the same as embodiment 1.
Example 5
The main road compressor 1 is a variable frequency scroll compressor, and the auxiliary road compressor 15 is a variable frequency rolling rotor compressor; the indoor side heat exchanger 12 is an air-cooled heat exchanger; the outdoor heat exchanger 4-1 is a laminated heat exchanger; the outdoor fan 4-2 is a variable frequency fan; the first expansion valve 9 is a manual expansion valve, and the second expansion valve 11 is a floating ball type expansion valve; the evaporating pressure regulator 14 is a proportional-differential regulator controlled by the pressure before the valve (i.e., evaporating pressure); the sub-cooler 6 is a flash tank. The other structure is the same as embodiment 1.
Example 6
The main road compressor 1 is a variable frequency rolling rotor compressor, and the auxiliary road compressor 15 is a constant frequency rolling rotor compressor; the indoor side heat exchanger 12 is an air-cooled heat exchanger; the outdoor heat exchanger 4-1 is a finned tube heat exchanger; the outdoor fan 4-2 is a variable frequency fan; the first expansion valve 9 is a manual expansion valve, and the second expansion valve 11 is a thermal expansion valve; the evaporating pressure regulator 14 is a proportional-integral-derivative regulator controlled by the pressure before the valve (i.e., evaporating pressure); the subcooler 6 is a double pipe heat exchanger. The other structure is the same as embodiment 1.
According to the invention, through the ingenious switching combination of the four-way reversing valve and the six one-way valves and the auxiliary optimization regulation of the auxiliary compressor and the evaporation pressure regulator, the air-cooled heat pump unit can realize six working modes:
(1) single stage compression refrigeration mode of operation
FIG. 2 is a flow chart of a single stage compression refrigeration mode of operation that can be used when the outdoor air temperature in the summer is between about 30℃ and 45℃. At the moment, a pump or a fan which is arranged on the main path compressor 1, the outdoor side fan 4-2 and the indoor side heat exchanger 12 in a matching way is started, and the auxiliary path compressor 15 is closed. The work flow of the system is as follows: the high-temperature high-pressure gas refrigerant discharged by the main path compressor 1 enters an exhaust inlet of a four-way reversing valve 3 through a main path oil separator 2 and a fifth one-way valve 5-5 in sequence, after the high-temperature high-pressure gas refrigerant is switched by the four-way reversing valve 3, the high-temperature high-pressure gas refrigerant enters an outdoor heat exchanger 4-1 to release heat to heat outdoor air introduced by an outdoor fan 4-2, the outdoor air is condensed into super-cooled or saturated liquid refrigerant, then enters a first expansion valve 9 through a first one-way valve 5-1, a recooler 6, a drying filter 7 and an observation mirror 8 in sequence, is changed into medium-temperature and medium-pressure gas-liquid two-phase refrigerant after being throttled and adjusted by the first expansion valve 9, enters a medium-pressure gas-liquid separator 10 to be subjected to gas-liquid separation, then the liquid refrigerant at the lower part of the medium-pressure gas-liquid separator 10 is changed into low-temperature and low-pressure gas-liquid two-phase refrigerant after being throttled and adjusted by a second expansion valve 11, and enters an indoor heat exchanger 12 through the third one-way valve 5-3 to absorb heat of secondary refrigerant introduced by a pump or a fan, the refrigerant is evaporated into low-pressure superheated refrigerant steam, and then enters a low-pressure gas-liquid separator 13 for gas-liquid separation after being switched by a four-way reversing valve 3, and the separated low-pressure gaseous refrigerant enters an air suction port of a main path compressor 1, is compressed by the main path compressor 1, is discharged into high-temperature high-pressure gaseous refrigerant, and starts to enter the next cycle.
(2) Three pressure refrigeration mode of operation
FIG. 3 is a flow chart of a three-pressure cooling mode of operation that can be used when the outdoor air temperature in the summer is between about 46℃ and about 55℃. At the moment, the pump or the fan which is matched and arranged on the main path compressor 1, the auxiliary path compressor 15, the outdoor side fan 4-2 and the indoor side heat exchanger 12 is started. The work flow of the system is as follows: the high-temperature high-pressure gaseous refrigerant discharged by the main path compressor 1 sequentially passes through the main path oil separator 2 and the fifth one-way valve 5-5 to be mixed with the high-temperature high-pressure gaseous refrigerant passing through the sixth one-way valve 5-6, then enters an exhaust inlet of the four-way reversing valve 3, is switched by the four-way reversing valve 3, enters the outdoor heat exchanger 4-1 to release heat to heat outdoor air introduced by the outdoor side fan 4-2, is condensed into supercooled or saturated liquid refrigerant, then enters the main path side of the sub-cooler 6 through the first one-way valve 5-1 to release heat to heat medium-pressure medium-temperature saturated gaseous refrigerant passing through the auxiliary path side of the sub-cooler 6, is further supercooled into liquid refrigerant with higher supercooling degree, then sequentially passes through the drying filter 7 and the observation mirror 8 to enter the first expansion valve 9, and is throttled and adjusted by the first medium-temperature expansion valve 9 to become medium-pressure gas-liquid two-phase refrigerant, the refrigerant enters a middle-pressure gas-liquid separator 10 to be subjected to gas-liquid separation and then is divided into two paths, wherein one path is a separated middle-pressure middle-temperature saturated liquid refrigerant, is discharged from the lower part of the middle-pressure gas-liquid separator 10, then is subjected to throttling regulation by a second expansion valve 11 to be changed into a low-temperature low-pressure gas-liquid two-phase refrigerant, enters an indoor side heat exchanger 12 through a third one-way valve 5-3 to absorb secondary refrigerant heat introduced by a pump or a fan, is evaporated into low-pressure superheated refrigerant steam, then enters a low-pressure gas-liquid separator 13 to be subjected to gas-liquid separation after being switched by a four-way reversing valve 3, enters an air suction port of a main path compressor 1, is compressed by the main path compressor 1 to discharge a high-temperature high-pressure gas refrigerant, and starts to enter the next cycle; the other path is separated medium-pressure and medium-temperature saturated gaseous refrigerant, the separated medium-pressure and medium-temperature saturated gaseous refrigerant is discharged from the upper part of the medium-pressure gas-liquid separator 10, enters the auxiliary path side of the recooler 6 to absorb the heat of the supercooled or saturated liquid refrigerant passing through the main path side of the recooler 6, is changed into medium-pressure superheated gaseous refrigerant, is throttled and regulated by the evaporation pressure regulator 14 to be changed into low-pressure superheated gas refrigerant, then enters the air suction port of the auxiliary path compressor 15, is compressed by the auxiliary path compressor 15 to discharge high-temperature and high-pressure gaseous refrigerant, and then sequentially passes through the auxiliary path oil separator 16 and the sixth one-way valve 5-6 to start entering the next cycle.
(3) Single stage compression heating mode of operation
Fig. 4 is a flow chart of a single-stage compression heating operation mode that can be used when the outdoor air temperature is between about-5 c and about 15 c in winter. At the moment, a pump or a fan which is arranged on the main path compressor 1, the outdoor side fan 4-2 and the indoor side heat exchanger 12 in a matching way is started, and the auxiliary path compressor 15 is closed. The work flow of the system is as follows: the high-temperature high-pressure gaseous refrigerant discharged from the main path compressor 1 enters an exhaust inlet of a four-way reversing valve 3 through a main path oil separator 2 and a fifth one-way valve 5-5, is switched by the four-way reversing valve 3, enters an indoor side heat exchanger 12 to release heat to heat secondary refrigerant introduced by a pump or a fan, is condensed into supercooled or saturated liquid refrigerant, then enters a first expansion valve 9 through a fourth one-way valve 5-4, a recooler 6, a drying filter 7 and an observation mirror 8 in sequence, is changed into medium-temperature and medium-pressure gas-liquid two-phase refrigerant after being throttled and adjusted by the first expansion valve 9, enters a medium-pressure gas-liquid separator 10 to be subjected to gas-liquid separation, then the liquid refrigerant at the lower part of the medium-pressure gas-liquid separator 10 is changed into low-temperature and low-pressure gas-liquid two-phase refrigerant after being throttled and adjusted by a second expansion valve 11, enters an outdoor side heat exchanger 4-1 through the second one-way valve 5-2 to absorb outdoor air heat introduced by an outdoor side fan 4-2, the refrigerant is evaporated into low-pressure superheated refrigerant steam, and then enters a low-pressure gas-liquid separator 13 for gas-liquid separation after being switched by a four-way reversing valve 3, and the separated low-pressure gaseous refrigerant enters an air suction port of a main path compressor 1, is compressed by the main path compressor 1, is discharged into high-temperature high-pressure gaseous refrigerant, and starts to enter the next cycle.
(4) Three-pressure heating working mode
FIG. 5 is a flow chart of a three-pressure heating operation mode, which can be adopted when the outdoor air temperature is about-20 to-6 ℃ in winter. At the moment, the pump or the fan which is matched and arranged on the main path compressor 1, the auxiliary path compressor 15, the outdoor side fan 4-2 and the indoor side heat exchanger 12 is started. The work flow of the system is as follows: the high-temperature high-pressure gaseous refrigerant discharged by the main path compressor 1 sequentially passes through the main path oil separator 2 and the fifth one-way valve 5-5 to be mixed with the high-temperature high-pressure gaseous refrigerant passing through the sixth one-way valve 5-6, then enters an exhaust inlet of the four-way reversing valve 3, is switched by the four-way reversing valve 3, enters the indoor side heat exchanger 12 to release heat to heat secondary refrigerant introduced by a pump or a fan, is condensed into supercooled or saturated liquid refrigerant, then enters the main path side of the recooler 6 through the fourth one-way valve 5-4 to release heat to heat medium-pressure medium-temperature saturated gaseous refrigerant passing through the auxiliary path side of the recooler 6, is further supercooled into liquid refrigerant with high supercooling degree, then sequentially passes through the drying filter 7 and the observation mirror 8 to enter the first expansion valve 9, and is throttled and adjusted by the first expansion valve 9 to become medium-temperature medium-pressure gas-liquid two-phase refrigerant, the refrigerant enters a middle-pressure gas-liquid separator 10 to be subjected to gas-liquid separation and then is divided into two paths, wherein one path is a separated middle-pressure middle-temperature saturated liquid refrigerant, is discharged from the lower part of the middle-pressure gas-liquid separator 10, is then changed into a low-temperature low-pressure gas-liquid two-phase refrigerant after being subjected to throttling regulation by a second expansion valve 11, enters an outdoor heat exchanger 4-1 through a second one-way valve 5-2 to absorb outdoor air heat introduced by an outdoor fan 4-2, is evaporated into low-pressure superheated refrigerant steam, then enters a low-pressure gas-liquid separator 13 to be subjected to gas-liquid separation after being switched by a four-way reversing valve 3, enters an air suction port of a main path compressor 1, is compressed by the main path compressor 1 to discharge a high-temperature high-pressure gas refrigerant, and starts to enter the next cycle; the other path is separated medium-pressure medium-temperature saturated gaseous refrigerant, the separated medium-pressure medium-temperature saturated gaseous refrigerant is discharged from the upper part of the medium-pressure gas-liquid separator 10, enters the auxiliary path side of the recooler 6 to absorb the heat of the supercooled or saturated liquid refrigerant passing through the main path side of the recooler 6, is changed into medium-pressure superheated gaseous refrigerant, is throttled and regulated by the evaporation pressure regulator 14 to be changed into low-pressure superheated gas refrigerant, then enters the air suction port of the auxiliary path compressor 15, is compressed by the auxiliary path compressor 15 to discharge high-temperature high-pressure gaseous refrigerant, and then sequentially passes through the auxiliary path oil separator 16 and the sixth one-way valve 5-6 to start entering the next cycle.
(5) Indoor cold-feeling-free rapid defrosting working mode
Fig. 6 is a flow chart of an indoor cold-feeling-free rapid defrosting operation mode, which can be adopted when the outdoor air humidity is high and the frosting of the outdoor heat exchanger 4-1 is severe in winter. At the moment, the auxiliary compressor 15 is started, and the pump or the fan which is matched with the main compressor 1, the outdoor side fan 4-2 and the indoor side heat exchanger 12 is closed. The work flow of the system is as follows: the high-temperature high-pressure gaseous refrigerant discharged by the auxiliary compressor 15 enters an exhaust inlet of a four-way reversing valve 3 through an auxiliary oil separator 2 and a sixth one-way valve 5-6 in sequence, after being switched by the four-way reversing valve 3, enters an outdoor heat exchanger 4-1 to release heat to heat frost on the outer surface of the heat exchanger, is condensed into supercooled or saturated liquid refrigerant, then enters a main side of a recooler 6 through a first one-way valve 5-1 to release heat to heat medium-pressure medium-temperature saturated gaseous refrigerant passing through an auxiliary side of the recooler 6, is further supercooled into liquid refrigerant with larger supercooling degree, then enters a first expansion valve 9 through a drying filter 7 and an observation mirror 8 in sequence, is throttled and adjusted by the first expansion valve 9 to become medium-temperature medium-pressure gas-liquid two-phase refrigerant, enters a medium-pressure gas-liquid separator 10 to carry out gas-liquid separation, and the separated medium-pressure medium-temperature saturated gaseous refrigerant, the refrigerant is discharged from the upper part of the medium-pressure gas-liquid separator 10, enters the auxiliary path side of the sub-cooler 6 to absorb the heat of the supercooled or saturated liquid refrigerant passing through the main path side of the sub-cooler 6, is changed into superheated gaseous refrigerant, is changed into low-pressure superheated gas refrigerant through throttling and pressure regulating of the evaporation pressure regulator 14, enters the air suction port of the auxiliary path compressor 15, is compressed by the auxiliary path compressor 15 to discharge high-temperature high-pressure gaseous refrigerant, and then sequentially passes through the auxiliary path oil separator 16 and the sixth one-way valve 5-6 to start entering the next cycle.
(6) Three-pressure quick defrosting work mode
Fig. 7 is a flow chart of a three-pressure fast defrosting operation mode, which can be adopted when the outdoor air humidity is very high and the frosting of the outdoor heat exchanger 4-1 is very serious in winter. At the moment, the main path compressor 1 and the auxiliary path compressor 15 are started, and the pump or the fan which is installed in a matching way for the outdoor side fan 4-2 and the indoor side heat exchanger 12 is closed. The work flow of the system is as follows: the high-temperature high-pressure gaseous refrigerant discharged by the main path compressor 1 sequentially passes through the main path oil separator 2 and the fifth one-way valve 5-5 to be mixed with the high-temperature high-pressure gaseous refrigerant passing through the sixth one-way valve 5-6, then enters an exhaust inlet of the four-way reversing valve 3, is switched by the four-way reversing valve 3, enters the outdoor side heat exchanger 4-1 to release heat to heat frost on the outer surface of the heat exchanger, is condensed into supercooled or saturated liquid refrigerant, then enters the main path side of the recooler 6 through the first one-way valve 5-1 to release heat to heat the medium-pressure medium-temperature saturated gaseous refrigerant passing through the auxiliary path side of the recooler 6, is further supercooled into liquid refrigerant with higher supercooling degree, then sequentially passes through the drying filter 7 and the observation mirror 8 to enter the first expansion valve 9, and is throttled and adjusted by the first expansion valve 9 to become medium-temperature medium-pressure gas-liquid two-phase refrigerant, the refrigerant enters a middle-pressure gas-liquid separator 10 to be subjected to gas-liquid separation and then is divided into two paths, wherein one path is a separated middle-pressure middle-temperature saturated liquid refrigerant, is discharged from the lower part of the middle-pressure gas-liquid separator 10, then is subjected to throttling regulation by a second expansion valve 11 to be changed into a low-temperature low-pressure gas-liquid two-phase refrigerant, enters an indoor side heat exchanger 12 through a third one-way valve 5-3 to absorb heat of indoor side refrigerant, is evaporated into low-pressure superheated refrigerant steam, then enters a low-pressure gas-liquid separator 13 to be subjected to gas-liquid separation after being switched by a four-way reversing valve 3, enters an air suction port of a main path compressor 1, is compressed by the main path compressor 1 to discharge a high-temperature high-pressure gas refrigerant, and starts to enter the next cycle; the other path is separated medium-pressure medium-temperature saturated gaseous refrigerant, the separated medium-pressure medium-temperature saturated gaseous refrigerant is discharged from the upper part of the medium-pressure gas-liquid separator 10, enters the auxiliary path side of the recooler 6 to absorb the heat of the supercooled or saturated liquid refrigerant passing through the main path side of the recooler 6, is changed into superheated gaseous refrigerant, is throttled and regulated by the evaporation pressure regulator 14 to be changed into low-pressure superheated gas refrigerant, then enters the air suction port of the auxiliary path compressor 15, is compressed by the auxiliary path compressor 15 to discharge high-temperature high-pressure gaseous refrigerant, and then sequentially passes through the auxiliary path oil separator 16 and the sixth one-way valve 5-6 to start entering the next cycle.
Claims (10)
1. The utility model provides a high-efficient air-cooled heat pump set of three pressure suitable for big difference in temperature which characterized in that: the system comprises a main path compressor (1), a main path oil separator (2), a four-way reversing valve (3), an outdoor side heat exchanger (4-1), a first one-way valve (5-1), a second one-way valve (5-2), a third one-way valve (5-3), a fourth one-way valve (5-4), a recooler (6), a medium pressure gas-liquid separator (10), a second expansion valve (11), an indoor side heat exchanger (12), a low pressure gas-liquid separator (13), an evaporation pressure regulator (14), an auxiliary path compressor (15), an auxiliary path oil separator (16) and a connecting pipeline; the exhaust port of the main path compressor (1) is connected with a four-way reversing valve (3) through a main path oil separator (2), the four-way reversing valve (3) is respectively connected with an outdoor side heat exchanger (4-1) and an indoor side heat exchanger (12) through connecting pipelines, the interface of the low-pressure gas-liquid separator (13) is connected, the other interface of the low-pressure gas-liquid separator (13) is connected with the air suction port of the main-path compressor (1), the other interface of the outdoor heat exchanger (4-1) is connected with the inlet of the first one-way valve (5-1) and the outlet of the second one-way valve (5-2), the outlet of the first one-way valve (5-1) is connected with the main-path inlet of the recooler (6) after being converged with the outlet of the fourth one-way valve (5-4), and the main-path outlet of the recooler (6) is connected with the inlet of the medium-pressure gas-liquid separator (10); two outlets of the medium-pressure gas-liquid separator (10) are respectively connected with a bypass inlet of the recooler (6) and an inlet of the second expansion valve (11); an outlet of the second expansion valve (11) is connected with an inlet of the second one-way valve (5-2) and an inlet of the third one-way valve (5-3), and an outlet of the third one-way valve (5-3) and an inlet of the fourth one-way valve (5-4) are converged through a connecting pipeline and then are connected with the other interface of the indoor side heat exchanger (12); and an auxiliary path outlet of the recooler (6) is connected with an air suction port of an auxiliary path compressor (15) after passing through the evaporation pressure regulator (14), and an air exhaust port of the auxiliary path compressor (15) is connected with an auxiliary path oil separator (16).
2. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference according to claim 1, characterized in that: the outdoor fan is characterized by also comprising an outdoor fan (4-2), a fifth one-way valve (5-5), a sixth one-way valve (5-6), a drying filter (7), an observation mirror (8) and a first expansion valve (9); the outdoor fan (4-2) is positioned at the outer side of the outdoor heat exchanger (4-1), the main path oil separator (2) is connected with the four-way reversing valve (3) through a fifth one-way valve (5-5), and the auxiliary path oil separator (16) is connected with the four-way reversing valve (3) through a sixth one-way valve (5-6); all the parts are connected through connecting pipelines; a connecting pipeline between the recooler (6) and the medium-pressure gas-liquid separator (10) is sequentially provided with a drying filter (7), an observation mirror (8) and a first expansion valve (9).
3. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference according to claim 1, characterized in that: and a T-shaped three-way pipeline is formed by connecting pipelines among the second expansion valve (11), the second one-way valve (5-2) and the third one-way valve (5-3).
4. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference according to claim 1, characterized in that: the main path compressor (1) and the auxiliary path compressor (15) are respectively in any one form of a fixed frequency scroll compressor, a fixed frequency rolling rotor compressor, a variable frequency scroll compressor and a variable frequency rolling rotor compressor.
5. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference according to claim 1, characterized in that: the indoor side heat exchanger (12) is in any structural form of an air-cooled heat exchanger and a water-cooled heat exchanger.
6. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference according to claim 1, characterized in that: the outdoor heat exchanger (4-1) is in any structural form of finned tube type, stacked type and parallel flow type heat exchangers.
7. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference as claimed in claim 2, wherein: the outdoor fan (4-2) is any one of a variable frequency fan, a fixed frequency fan and a gear shifting fan.
8. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference as claimed in claim 2, wherein: the first expansion valve (9) and the second expansion valve (11) are in the form of any one of a manual expansion valve, a choke expansion valve, a floating ball type expansion valve, a thermal expansion valve and an electronic expansion valve.
9. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference according to claim 1, characterized in that: the evaporation pressure regulator (14) is in the form of any one of a proportional regulator, a proportional integral regulator, a proportional derivative regulator and a proportional integral derivative regulator which are controlled by the pressure before the valve.
10. The three-pressure high-efficiency air-cooled heat pump unit suitable for the large temperature difference according to claim 1, characterized in that: the recooler (6) is in any structural form of a plate heat exchanger, a double-pipe heat exchanger and a flash tank.
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| CN110243083B (en) * | 2019-06-28 | 2024-07-16 | 中原工学院 | Energy-storage type efficient air source solar composite heat pump water heater |
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