CN109520170B - Air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions - Google Patents

Air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions Download PDF

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Publication number
CN109520170B
CN109520170B CN201811432959.7A CN201811432959A CN109520170B CN 109520170 B CN109520170 B CN 109520170B CN 201811432959 A CN201811432959 A CN 201811432959A CN 109520170 B CN109520170 B CN 109520170B
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liquid
gas
valve
heat exchanger
supercooling
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CN109520170A (en
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崔四齐
王聪民
裴华强
徐铚成
桑翎
张俊山
李旭阁
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Zhongyuan University of Technology
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Zhongyuan University of Technology
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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
    • 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
    • F25B40/02—Subcoolers
    • 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
    • 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
    • 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
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Abstract

The invention provides an air source heat pump unit with two-stage supercooling and liquid pulse defrosting functions, which comprises a refrigeration compressor, a four-way reversing valve, an outdoor heat exchanger, a gas-liquid separator for a condenser, a supercooling coil, a heat regenerator, an electronic expansion valve, an indoor heat exchanger, a gas-liquid separator for an evaporator, an air suction pressure regulating valve, a supercooling gas-liquid separator, a one-way valve, a pulse defrosting regulating valve, a PLC (programmable logic controller), a temperature sensor, a pressure sensor, a connecting pipeline and a wire. According to the invention, through the ingenious structural design of the outdoor heat exchanger and the indoor heat exchanger with the gas-liquid separator, the primary supercooling of the supercooling type gas-liquid separator, the secondary supercooling of the heat regenerator and the intelligent control of the pulse defrosting regulating valve, the refrigerating output/heating output and the energy efficiency ratio of the heat pump unit during high-temperature refrigeration and low-temperature heating are improved, the rapid melting of the frost layer on the surface of the outdoor heat exchanger in winter is realized under the condition of completely not influencing the indoor heating effect, and the high-efficiency and reliable operation of the heat pump unit under the working condition of a wide temperature area is ensured.

Description

Air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions
Technical Field
The invention relates to the technical field of air-conditioning heat pumps, in particular to an air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions.
Background
In the face of the increasingly prominent problems of energy shortage and environmental pollution, the development of an air-conditioning heat pump device with high efficiency, energy conservation, good comfort, safety and reliability 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, 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 the evaporator is frosted seriously, the compression ratio of the 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 defects of long defrosting time, poor effect, influence on indoor continuous heat supply and the like are caused. In short, when the outdoor temperature is too high or too low, the conventional air source heat pump has the above outstanding problems, which seriously affects the popularization and application of the air source heat pump.
Aiming at the defects of the conventional air source heat pump device, the current common solutions are three types: the air source heat pump air-conditioning system comprises a medium-pressure air-supplementing quasi-two-stage compression refrigeration/heating cycle, a two-stage compression refrigeration/heating cycle and a cascade refrigeration/heating cycle, and solves the problems of overlarge compression ratio and overhigh exhaust temperature of a compressor when air source heat pumps are used for refrigerating under a high-temperature working condition or heating under a low-temperature working condition to a certain extent, improves the refrigeration/heating capacity and the energy efficiency ratio of a unit, and has the following problems: the 'quasi-two-stage compression' refrigeration/heating circulation for medium-pressure air supplement needs to adopt a refrigeration compressor with an air supplement function, and the optimal control of the air supplement amount needs to be researched. The two-stage compression type refrigeration/heating cycle and the cascade type refrigeration/heating cycle adopt two refrigeration compressors and two throttle expansion valves, so that the system has the advantages of large circulation power consumption, low efficiency, high cost and excessively complex control, and is generally used for a refrigeration and cold storage unit. In addition, when the outdoor heat exchanger frosts in winter, the quasi-two-stage compression refrigeration/heating cycle and the two-stage compression refrigeration/heating cycle of medium-pressure air supplement often adopt a reverse cycle defrosting mode, which can affect the continuous heat supply of the indoor user side, while the cascade refrigeration/heating cycle often adopts a hot gas bypass defrosting mode, but when the defrosting speed is not fast enough, the compressor can enter a protective shutdown state or generate a liquid impact phenomenon, and meanwhile, in the defrosting process, the heat supply quantity of the indoor user side can be affected due to the reduction of the air inflow of the condenser.
Disclosure of Invention
The invention aims to provide an air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions, and the air source heat pump unit is used for solving the outstanding technical problems that the compression ratio of a compressor is overlarge, the exhaust temperature is overhigh, the surface of an evaporator is easy to frost, the defrosting efficiency is low, the refrigerating capacity/heating capacity and energy efficiency ratio of a system are sharply reduced and the like when the conventional air source heat pump is used for refrigerating under a high-temperature working condition and heating under a low-temperature working condition. The air source heat pump unit can be widely applied to all places which can adopt the air source heat pump, such as civil buildings, public buildings, villa buildings and the like.
The technical scheme of the invention is realized as follows:
an air source heat pump unit with two-stage supercooling and liquid pulse defrosting functions comprises an air source heat pump subsystem and an automatic control subsystem, wherein the air source heat pump subsystem comprises a refrigeration compressor, a four-way reversing valve, an outdoor heat exchanger, a gas-liquid separator for a condenser, an outdoor fan, a high-pressure bypass electromagnetic valve, a liquid storage device, a supercooling coil, a heat regenerator, a drying filter, an electronic expansion valve, an indoor heat exchanger, a gas-liquid separator for an evaporator, an indoor fan, a low-pressure bypass electromagnetic valve, an air suction pressure regulating valve, a supercooling type gas-liquid separator, a first check valve, a second check valve, a third check valve, a fourth check valve, a pulse defrosting regulating valve and a connecting pipeline; the specific connection relationship of the air source heat pump subsystem is as follows: the air outlet of the refrigeration compressor is respectively connected with the corresponding interfaces of the outdoor heat exchanger, the indoor heat exchanger, the low-pressure bypass electromagnetic valve and the air suction pressure regulating valve through a four-way reversing valve and a corresponding connecting pipeline, other interfaces of the outdoor heat exchanger are respectively connected with the gas-liquid inlet and the gas outlet of the gas-liquid separator for the condenser, the inlet of the first one-way valve, the outlet of the second one-way valve and the outlet of the pulse defrosting regulating valve, other interfaces of the indoor heat exchanger are respectively connected with the gas-liquid inlet and the liquid outlet of the gas-liquid separator for the evaporator, the inlet of the third one-way valve, the outlet of the fourth one-way valve and the inlet of the pulse defrosting regulating valve, the liquid outlet of the gas-liquid separator for the condenser is connected with the inlet of the liquid storage device through a high-pressure bypass electromagnetic valve, other interfaces of the liquid storage device are respectively connected with the outlets of the first one-way valve and the third one-way valve and the inlet of the supercooling coil, the supercooling coil is arranged at the lower side inside of the supercooling gas-liquid separator, the outlet of the main circuit of the regenerator is connected with the inlet of the drying filter, the gas-liquid separator for the evaporator is respectively connected with the inlet of the four-way reversing valve and the inlet of the air suction pressure regulating valve, and the inlet of the bypass electromagnetic valve of the four-way reversing valve.
The automatic control subsystem comprises a PLC controller, a temperature sensor, a pressure sensor, a valve piece, an actuator of equipment and a connecting wire. The specific installation connection relationship of the automatic control subsystem is as follows: the PLC is connected with an actuator of the equipment through a temperature sensor, a pressure sensor and a valve respectively by leads; and the temperature sensor and the pressure sensor are arranged on a pipeline of an outlet of the supercooling type gas-liquid separator.
The refrigeration compressor is preferably any one of a fixed-frequency scroll compressor, a fixed-frequency rolling rotor compressor, a variable-frequency scroll compressor and a variable-frequency rolling rotor compressor.
Preferably, the outdoor heat exchanger and the indoor heat exchanger are in any one structural form of a finned tube heat exchanger, a stacked heat exchanger and a parallel flow heat exchanger.
Preferably, the middle part of the outdoor heat exchanger is provided with a gas-liquid outlet and a gas inlet which are respectively connected with the gas-liquid inlet and the gas outlet of the gas-liquid separator for the condenser.
Preferably, the middle part of the indoor side heat exchanger is provided with a gas-liquid outlet and a liquid inlet which are respectively connected with the gas-liquid inlet and the liquid outlet of the gas-liquid separator for the evaporator.
Preferably, the outdoor side fan and the indoor side fan are in any one form of a variable frequency fan, a fixed frequency fan and a gear shifting fan.
Preferably, the regenerator is in any structural form of a plate heat exchanger, a double-pipe heat exchanger and a shell-and-tube heat exchanger.
The invention provides an air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions, which has novel conception and skillful unit design optimization, and has the following advantages and outstanding effects compared with the prior art:
(1) By the ingenious structural design of the outdoor heat exchanger with the gas-liquid separator and the indoor heat exchanger, when the refrigerating working condition is operated, the outdoor heat exchanger is ensured not to store high-pressure supercooled liquid, and the indoor heat exchanger is ensured not to store low-pressure superheated gas, so that the heat exchange efficiency of the outdoor heat exchanger and the indoor heat exchanger is improved, the pressure drop loss of the heat exchangers is reduced, the evaporation temperature of a unit is improved, the condensation temperature of the unit is reduced, and the refrigerating capacity and the energy efficiency ratio of the system are increased.
(2) Through the primary supercooling of the supercooling type gas-liquid separator and the secondary supercooling of the heat regenerator, the irreversible loss of a refrigerant passing through the electronic expansion valve and the inlet dryness of the evaporator are reduced, the refrigerating capacity of the heat pump unit under the high-temperature working condition and the heating capacity of the heat pump unit under the low-temperature working condition are improved, and the high-efficiency and reliable operation of the heat pump unit under the working condition of a wide temperature area is ensured.
(3) When the defrosting mode is operated in winter, the high-temperature high-pressure liquid refrigerant from the indoor side heat exchanger enters the outdoor side heat exchanger at intervals through the intelligent control of the pulse defrosting regulating valve, a large amount of heat is released in a short time to generate heat impulse, the quick melting of a frost layer on the surface of the outdoor side heat exchanger is realized, and meanwhile, the indoor heating effect is not influenced completely.
(4) Through the intelligent throttling regulation of the air suction pressure regulating valve, the problem that the air suction pressure of a compressor is too high or liquid impact is generated when the heat pump unit adopts liquid pulse defrosting is solved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic diagram of the structure of the present invention.
Fig. 2 is a flow chart of a cooling operation mode.
Fig. 3 is a flow chart of a heating operation mode.
Fig. 4 is a flow chart of the liquid pulse defrosting operation mode.
The numbers and names of the components in the figures are as follows: the system comprises a 1-refrigeration compressor, a 2-four-way reversing valve, a 3-outdoor heat exchanger, a 4-condenser gas-liquid separator, a 5-outdoor fan, a 6-high-pressure bypass electromagnetic valve, a 7-liquid reservoir, an 8-supercooling coil, a 9-heat regenerator, a 10-drying filter, an 11-electronic expansion valve, a 12-indoor heat exchanger, a 13-evaporator gas-liquid separator, a 14-indoor fan, a 15-low-pressure bypass electromagnetic valve, a 16-suction pressure regulating valve, a 17-supercooling gas-liquid separator, an 18-first one-way valve, a 19-second one-way valve, a 20-third one-way valve, a 21-fourth one-way valve, a 22-pulse defrosting regulating valve, a 23-PLC (programmable logic controller), a 24-temperature sensor and a 25-pressure sensor.
Detailed Description
The technical solutions of the present invention will be described clearly and completely below with reference to embodiments of the present invention, and it should be apparent that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without inventive effort based on the embodiments of the present invention, are within the scope of the present invention.
As shown in fig. 1, the invention provides a high-efficiency air source heat pump unit suitable for wide-temperature-zone working conditions, which comprises an air source heat pump subsystem and an automatic control subsystem, wherein the air source heat pump subsystem comprises a refrigeration compressor 1, a four-way reversing valve 2, an outdoor heat exchanger 3, an air-liquid separator 4 for a condenser, an outdoor fan 5, a high-pressure bypass electromagnetic valve 6, a liquid reservoir 7, a supercooling coil 8, a heat regenerator 9, a drying filter 10, an electronic expansion valve 11, an indoor heat exchanger 12, an air-liquid separator 13 for an evaporator, an indoor fan 14, a low-pressure bypass electromagnetic valve 15, an air suction pressure regulating valve 16, a supercooling type air-liquid separator 17, a first check valve 18, a second check valve 19, a third check valve 20, a fourth check valve 21, a pulse defrosting regulating valve 22 and a connecting pipeline, and the specific connection relationship of the air source heat pump subsystem is as follows: the air outlet of the refrigeration compressor 1 is respectively connected with the corresponding interfaces of an outdoor heat exchanger 3, an indoor heat exchanger 12, a low-pressure bypass electromagnetic valve 15 and an air suction pressure regulating valve 16 through a four-way reversing valve 2 and a corresponding connecting pipeline, other interfaces of the outdoor heat exchanger 3 are respectively connected with a gas-liquid inlet and a gas outlet of an air-liquid separator 4 for a condenser, an inlet of a first one-way valve 18, an outlet of a second one-way valve 19 and an outlet of a pulse defrosting regulating valve 22, other interfaces of the indoor heat exchanger 12 are respectively connected with a gas-liquid inlet and a liquid outlet of an air-liquid separator 13 for an evaporator, an inlet of a third one-way valve 20, an outlet of a fourth one-way valve 21 and an inlet of the pulse defrosting regulating valve 22, a liquid outlet of the air-liquid separator 4 for the condenser is connected with an inlet of a liquid storage 7 through a high-pressure bypass electromagnetic valve 6, other interfaces of the liquid storage 7 are respectively connected with outlets of the first one-way valve 18 and the third one-way valve 20 and an inlet of a supercooling coil 8, a supercooling coil 8 is arranged at the lower side inside of a supercooling type gas-liquid separator 17, the outlet of the low-pressure bypass electromagnetic valve 15 is connected with one of the outlets of the four-way reversing valve 2 and the inlet of the suction pressure regulating valve 16, and the outlet of the suction pressure regulating valve 16 is connected with the air suction port of the refrigeration compressor 1 through the super-cooling type gas-liquid separator 17.
The automatic control subsystem comprises a PLC (programmable logic controller) 23, a temperature sensor 24, a pressure sensor 25, a valve, an actuator of equipment and a connecting wire, and the automatic control subsystem is specifically installed and connected in a way that: the PLC 23 is connected with the actuator of the device through the temperature sensor 24, the pressure sensor 25, the valve element and the wire, the temperature sensor 24 and the pressure sensor 25 are installed on the pipeline of the outlet of the super-cooling type gas-liquid separator 17.
Preferably, the refrigeration compressor 1 is any one of a fixed-frequency scroll compressor, a fixed-frequency rolling rotor compressor, an inverter scroll compressor, and an inverter rolling rotor compressor.
Preferably, the outdoor heat exchanger 3 and the indoor heat exchanger 12 are any one of a fin-tube heat exchanger, a stacked heat exchanger, and a parallel flow heat exchanger.
Preferably, the middle part of the outdoor heat exchanger 3 is provided with a gas-liquid outlet and a gas inlet which are respectively connected with the gas-liquid inlet and the gas outlet of the gas-liquid separator 4 for the condenser.
Preferably, the middle part of the indoor heat exchanger 12 is provided with a gas-liquid outlet and a liquid inlet, which are respectively connected with the gas-liquid inlet and the liquid outlet of the evaporator gas-liquid separator 13.
Preferably, the outdoor side fan 5 and the indoor side fan 14 are any one of a variable frequency fan, a fixed frequency fan and a gear shifting fan.
Preferably, the regenerator 9 is in any structural form of a plate heat exchanger, a double-tube heat exchanger and a shell-and-tube heat exchanger.
The invention can realize three working modes through the ingenious structural design of the outdoor heat exchanger and the indoor heat exchanger with the gas-liquid separator, the primary supercooling of the supercooling type gas-liquid separator, the secondary supercooling of the heat regenerator and the intelligent control of the pulse defrosting regulating valve:
(1) Refrigeration mode of operation
Fig. 2 is a flow chart of a refrigeration working mode, when the indoor temperature and humidity are high in summer, the PLC controller 23 selects the refrigeration working mode to operate, the refrigeration compressor 1, the outdoor side fan 5, the high-pressure bypass solenoid valve 6, the electronic expansion valve 11, the indoor side fan 14, the low-pressure bypass solenoid valve 15, and the suction pressure regulating valve 16 are started, and the electromagnetic head of the four-way reversing valve 2 and the pulse defrosting regulating valve 22 are closed. The workflow in this mode: the high-temperature high-pressure superheated gaseous refrigerant discharged from the refrigeration compressor 1 enters the outdoor heat exchanger 3 through the switching of the four-way reversing valve 2, releases heat to heat outdoor air introduced by the outdoor fan 5, is condensed into high-pressure gas-liquid two-phase refrigerant in the middle of the outdoor heat exchanger 3, then enters the condenser and the gas-liquid separator 4 for gas-liquid separation, returns the separated high-temperature high-pressure gaseous refrigerant to the outdoor heat exchanger 3 again for continuous condensation, then enters the liquid reservoir 7 through the first one-way valve 18, and the separated high-temperature high-pressure liquid refrigerant also enters the liquid reservoir 7 through the high-pressure bypass electromagnetic valve 6, and then the liquid refrigerant at the lower part of the liquid reservoir 7 enters the supercooling coil 8 at the bottom of the supercooling gas-liquid separator 17 to release heat to heat the liquid refrigerant separated by the supercooling gas-liquid separator 17, and is cooled into first-stage supercooling liquid refrigerant, the heat released by the heat regenerator 9 heats the low-temperature low-pressure refrigerant steam separated by the evaporator with the gas-liquid separator 13, the refrigerant steam is continuously cooled to become a secondary supercooled liquid refrigerant, then the refrigerant steam enters the electronic expansion valve 11 through the drying filter 10, is throttled and expanded to become a low-temperature low-pressure gas-liquid two-phase refrigerant, enters the indoor side heat exchanger 12 through the fourth one-way valve 21 to evaporate and absorb the heat of the indoor air introduced by the indoor side fan 14, the refrigerant steam is evaporated in the middle of the indoor side heat exchanger 12 to become a low-temperature low-pressure gas-liquid two-phase refrigerant, then the refrigerant steam enters the evaporator with the gas-liquid separator 13 to be subjected to gas-liquid separation, the separated low-temperature low-pressure liquid refrigerant returns to the indoor side heat exchanger 12 again to be continuously evaporated to become superheated refrigerant steam, then the refrigerant steam enters the suction pressure regulating valve 16 through the switching of the four-way reversing valve 2, and the separated low-temperature low-pressure refrigerant steam absorbs the heat of the primary supercooled liquid refrigerant from the supercooling coil 8 through the heat regenerator 9, the superheated refrigerant steam is changed into superheated refrigerant steam, then enters the suction pressure regulating valve 16 through the low-pressure bypass electromagnetic valve 15, the superheated refrigerant steam mixed by the superheated refrigerant steam and the suction pressure regulating valve 16 is throttled and regulated, then enters the supercooling type gas-liquid separator 17, the separated gaseous refrigerant enters the suction port of the refrigeration compressor 1, then the high-temperature high-pressure superheated gaseous refrigerant is discharged through the compression of the refrigeration compressor 1, and the next cycle is started. In the process of the refrigeration mode operation, the PLC 23 calculates the suction superheat degree of the refrigeration compressor 1 through temperature and pressure data transmitted by a temperature sensor 24 and a pressure sensor 25 which are arranged on an outlet pipeline of the supercooling type gas-liquid separator 17, and the suction superheat degree is used as a control signal to adjust the opening degree of the electronic expansion valve 11, so that the flow of refrigerant liquid entering the indoor side heat exchanger 12 is controlled to be matched with the refrigeration load, and the liquid impact phenomenon of the refrigeration compressor 1 is avoided. The PLC 23 adjusts the opening of the suction pressure regulating valve 16 by taking pressure data transmitted by a pressure sensor 25 arranged on an outlet pipeline of the super-cooling type gas-liquid separator 17 as a control signal, controls the suction pressure of the refrigeration compressor 1 and avoids the refrigeration compressor 1 from running under high suction pressure.
(2) Heating mode of operation
Fig. 3 is a flow chart of a heating operation mode, when the indoor temperature is relatively low in winter, at this time, the PLC controller 23 selects a heating operation mode to operate, the refrigeration compressor 1, the electromagnetic head of the four-way reversing valve 2, the outdoor fan 5, the electronic expansion valve 11, the indoor fan 14, and the suction pressure regulating valve 16 are started, and the high-pressure bypass electromagnetic valve 6, the low-pressure bypass electromagnetic valve 15, and the pulse defrosting regulating valve 22 are closed. The workflow in this mode: the high-temperature high-pressure superheated gaseous refrigerant discharged from the refrigeration compressor 1 enters the indoor side heat exchanger 12 through the switching of the four-way reversing valve 2, releases heat to heat indoor air introduced through the indoor side fan 14, is condensed into high-pressure liquid refrigerant, then sequentially passes through the third one-way valve 20 and the liquid reservoir 7 to enter the supercooling coil 8 at the bottom of the supercooling type gas-liquid separator 17, releases heat to heat the liquid refrigerant separated by the supercooling type gas-liquid separator 17, is cooled to become supercooled liquid refrigerant, then sequentially passes through the heat regenerator 9 and the drying filter 10 to enter the electronic expansion valve 11, is throttled and expanded to become low-temperature low-pressure gas-liquid two-phase refrigerant, then passes through the second one-way valve 19 to enter the outdoor side heat exchanger 3 to evaporate and absorb heat introduced into outdoor air through the outdoor side fan 5 to become low-temperature superheated steam, and then enters the suction pressure regulating valve 16 through the switching of the four-way reversing valve 2, is throttled and then enters the supercooling type gas-liquid separator 17, the separated gaseous refrigerant enters the air inlet of the refrigeration compressor 1, then is compressed and discharged into high-temperature high-pressure superheated gaseous refrigerant, and starts the next cycle. In the process of the refrigeration mode operation, the PLC 23 calculates the suction superheat degree of the refrigeration compressor 1 through temperature and pressure data transmitted by a temperature sensor 24 and a pressure sensor 25 which are arranged on an outlet pipeline of the supercooling type gas-liquid separator 17, and the suction superheat degree is used as a control signal to adjust the opening degree of the electronic expansion valve 11, so that the flow of refrigerant liquid entering the outdoor heat exchanger 3 is controlled to be matched with the refrigeration load, and the liquid impact phenomenon of the refrigeration compressor 1 is avoided. The PLC controller 23 adjusts the opening of the suction pressure adjusting valve 16 by using the pressure data transmitted from the pressure sensor 25 installed on the outlet line of the supercooling type gas-liquid separator 17 as a control signal, controls the suction pressure of the refrigeration compressor 1, and prevents the refrigeration compressor 1 from operating at a high suction pressure.
(3) Liquid pulse defrosting mode
Fig. 4 is a flow chart of a liquid pulse defrosting operation mode, when the outdoor air humidity is high and the outdoor heat exchanger 3 frosts seriously in winter, at this time, the PLC controller 23 selects the liquid pulse defrosting operation mode, the refrigeration compressor 1, the electromagnetic head of the four-way reversing valve 2, the indoor side fan 14, the suction pressure regulating valve 16 and the pulse defrosting regulating valve 22 are started, and the outdoor side fan 5, the high-pressure bypass electromagnetic valve 6, the electronic expansion valve 11 and the low-pressure bypass electromagnetic valve 15 are closed. Workflow in this mode: the high-temperature high-pressure superheated gaseous refrigerant discharged by the refrigeration compressor 1 enters the indoor side heat exchanger 12 through the switching of the four-way reversing valve 2, releases heat to heat indoor air introduced by the indoor side fan 14, is condensed into high-pressure liquid refrigerant, then enters the outdoor side heat exchanger 3 at intervals through the pulse defrosting regulating valve 22 to release heat to heat frost on the outer surface of the heat exchanger, is condensed into supercooled liquid refrigerant, enters the air suction pressure regulating valve 16 through the switching of the four-way reversing valve 2, is throttled and depressurized to become low-temperature low-pressure gas-liquid two-phase refrigerant, then enters the supercooling type gas-liquid separator 17 to carry out gas-liquid separation, the separated gaseous refrigerant enters the air suction port of the refrigeration compressor 1, is compressed by the refrigeration compressor 1 to discharge the high-temperature high-pressure superheated gaseous refrigerant, and starts the next cycle until a frost layer on the surface of the outdoor side heat exchanger 3 is completely dissolved. In the liquid pulse defrosting operation mode, the PLC controller 23 adjusts the switching frequency of the pulse defrosting control valve 22 by using the pressure data transmitted from the pressure sensor 25 installed on the outlet pipeline of the super-cooling type gas-liquid separator 17 as a control signal, and controls the flow rate of the high-temperature and high-pressure liquid refrigerant entering the outdoor heat exchanger 3, thereby realizing the rapid defrosting of the surface frost layer of the outdoor heat exchanger 3. The PLC controller 23 adjusts the opening of the suction pressure adjusting valve 16 by using the pressure data transmitted from the pressure sensor 25 installed on the outlet line of the supercooling type gas-liquid separator 17 as a control signal, controls the suction pressure of the refrigeration compressor 1, and prevents the refrigeration compressor 1 from operating at a high suction pressure.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and should not be taken as limiting the scope of the present invention, which is intended to cover any modifications, equivalents, improvements, etc. within the spirit and scope of the present invention.

Claims (8)

1. The utility model provides an air source heat pump set with doublestage is supercooled and liquid pulse defrosting function which characterized in that: the air source heat pump subsystem comprises a refrigeration compressor (1), a four-way reversing valve (2), an outdoor heat exchanger (3), a gas-liquid separator (4) for a condenser, an outdoor fan (5), a high-pressure bypass electromagnetic valve (6), a liquid storage device (7), a supercooling coil (8), a heat regenerator (9), a drying filter (10), an electronic expansion valve (11), an indoor heat exchanger (12), a gas-liquid separator (13) for an evaporator, an indoor fan (14), a low-pressure bypass electromagnetic valve (15), an air suction pressure regulating valve (16), a supercooling type gas-liquid separator (17), a first check valve (18), a second check valve (19), a third check valve (20), a fourth check valve (21), a pulse defrosting regulating valve (22) and a connecting pipeline, wherein an air outlet of the refrigeration compressor (1) is respectively connected with corresponding interfaces of the outdoor heat exchanger (3), the indoor heat exchanger (12), the low-pressure bypass electromagnetic valve (15) and the air suction pressure regulating valve (16) through the four-way reversing valve (2) and the corresponding connecting pipeline, other interfaces of the refrigeration compressor (3) are respectively connected with an inlet of the gas-liquid separator (4), an inlet of the gas-liquid separator, an inlet of the gas-liquid outlet of the first check valve (18), an inlet of the gas-liquid outlet of the second check valve (18) and a defrosting outlet of the second check valve (22), and a defrosting outlet of the outdoor heat exchanger (22), and a defrosting outlet of the second check valve of the outdoor heat exchanger (22) Other interfaces of the indoor side heat exchanger (12) are respectively connected with a gas-liquid inlet and a liquid outlet of the evaporator gas-liquid separator (13), an inlet of a third one-way valve (20), an outlet of a fourth one-way valve (21) and an inlet of a pulse defrosting regulating valve (22), a liquid outlet of the condenser gas-liquid separator (4) is connected with an inlet of a liquid storage device (7) through a high-pressure bypass electromagnetic valve (6), other interfaces of the liquid storage device (7) are respectively connected with outlets of the first one-way valve (18) and the third one-way valve (20) and an inlet of a supercooling coil (8), the supercooling coil (8) is arranged at the lower side inside the supercooling type gas-liquid separator (17), an outlet of the supercooling coil is connected with a main path inlet of a heat regenerator (9), a main path outlet, a loop inlet and a loop outlet of the heat regenerator (9) are respectively connected with an inlet of a drying filter (10), a gas outlet of the evaporator gas-liquid separator (13) is connected with an inlet of a low-pressure bypass electromagnetic valve (15), an outlet of the drying filter (10) is respectively connected with an inlet of a supercooling valve (19) through an electronic expansion valve (11), an inlet of a suction inlet of a four-way air suction air inlet of a refrigerating compressor (1), and a low-pressure regulating valve (16) of a four-way air-flow regulating valve (1) are respectively connected with an inlet of a refrigerating compressor (17), and a refrigerating compressor (1) of a refrigerating compressor (17), and a four-way bypass electromagnetic valve (16), wherein the bypass electromagnetic valve (1) and a bypass electromagnetic valve (1) is connected with a bypass electromagnetic valve (16) (ii) a
The high-temperature high-pressure superheated gaseous refrigerant discharged from the refrigeration compressor 1 enters the outdoor heat exchanger 3 through the switching of the four-way reversing valve 2, releases heat to heat outdoor air introduced by the outdoor fan 5, is condensed into high-pressure gas-liquid two-phase refrigerant in the middle of the outdoor heat exchanger 3, then enters the condenser and the gas-liquid separator 4 for gas-liquid separation, the separated high-temperature high-pressure gaseous refrigerant returns to the outdoor heat exchanger 3 for continuous condensation, then enters the liquid reservoir 7 through the first one-way valve 18, the separated high-temperature high-pressure liquid refrigerant also enters the liquid reservoir 7 through the high-pressure bypass solenoid valve 6, then the liquid refrigerant at the lower part of the liquid reservoir 7 enters the supercooling coil 8 at the bottom of the supercooling type gas-liquid separator 17 for heat heating of the separated liquid refrigerant by the supercooling type gas-liquid separator 17, is cooled to become first-stage supercooling liquid refrigerant, then the low-temperature low-pressure refrigerant is discharged from the heat regenerator 9 to heat the low-temperature low-pressure refrigerant separated by the evaporator gas-liquid separator 13, the second-stage supercooling liquid refrigerant enters the electronic expansion valve 11 through the gas-liquid drying filter 10, is throttled and expanded to become low-temperature low-pressure two-phase refrigerant, then enters the indoor heat regenerator 12 for continuous absorption of the indoor heat exchange evaporator 12 through the four-stage gas-liquid evaporator 12, and enters the low-liquid heat exchanger, and the low-temperature evaporator 12 for continuous absorption. The superheated refrigerant steam which is changed into the superheated refrigerant steam also enters the suction pressure regulating valve 16 through the low-pressure bypass electromagnetic valve 15, the superheated refrigerant steam mixed by the superheated refrigerant steam and the suction pressure regulating valve 16 is throttled and regulated and then enters the supercooling type gas-liquid separator 17, the separated gaseous refrigerant enters the suction port of the refrigeration compressor 1, the high-temperature high-pressure superheated gaseous refrigerant is discharged through the compression of the refrigeration compressor 1, and the next cycle is started; in the operation process of the refrigeration mode, the PLC 23 calculates the suction superheat degree of the refrigeration compressor 1 through temperature and pressure data transmitted by a temperature sensor 24 and a pressure sensor 25 which are arranged on an outlet pipeline of the supercooling type gas-liquid separator 17, adjusts the opening degree of the electronic expansion valve 11 by taking the suction superheat degree as a control signal, controls the flow of refrigerant liquid entering the indoor side heat exchanger 12 to be matched with refrigeration load, and avoids the liquid impact phenomenon of the refrigeration compressor 1; the PLC controller 23 adjusts the opening of the suction pressure adjusting valve 16 by using the pressure data transmitted from the pressure sensor 25 installed on the outlet line of the supercooling type gas-liquid separator 17 as a control signal, controls the suction pressure of the refrigeration compressor 1, and prevents the refrigeration compressor 1 from operating at a high suction pressure.
2. The air source heat pump unit with the double-stage supercooling and liquid pulse defrosting functions as claimed in claim 1, wherein: the automatic control subsystem comprises a PLC (programmable logic controller) 23, a temperature sensor 24, a pressure sensor 25, an actuator of a valve and equipment and a connecting lead, the PLC 23 is respectively connected with the temperature sensor 24, the pressure sensor 25 and the actuator of the valve and equipment through leads, and the temperature sensor 24 and the pressure sensor 25 are installed on a pipeline at an outlet of the super-cooling type gas-liquid separator 17.
3. The air source heat pump unit with dual-stage supercooling and liquid pulse defrosting functions according to claim 2, wherein: the refrigeration compressor (1) is any one of a fixed-frequency scroll compressor, a fixed-frequency rolling rotor compressor, a variable-frequency scroll compressor and a variable-frequency rolling rotor compressor.
4. The air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions as claimed in claim 2, wherein: the outdoor heat exchanger (3) and the indoor heat exchanger (12) are in any structural form of a finned tube type heat exchanger, a stacked type heat exchanger and a parallel flow type heat exchanger.
5. The air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions as claimed in claim 2, wherein: and a gas-liquid outlet and a gas inlet are formed in the middle of the outdoor heat exchanger (3) and are respectively connected with the gas-liquid inlet and the gas outlet of the gas-liquid separator (4) for the condenser.
6. The air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions as claimed in claim 2, wherein: and a gas-liquid outlet and a liquid inlet are formed in the middle of the indoor side heat exchanger (12) and are respectively connected with the gas-liquid inlet and the liquid outlet of the gas-liquid separator (13) for the evaporator.
7. The air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions as claimed in claim 2, wherein: the outdoor side fan (5) and the indoor side fan (14) are in any form of a variable frequency fan, a fixed frequency fan and a gear shifting fan.
8. The air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions as claimed in claim 2, wherein: the heat regenerator (9) is in any structural form of a plate heat exchanger, a double-pipe heat exchanger and a shell-and-tube heat exchanger.
CN201811432959.7A 2018-11-28 2018-11-28 Air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions Active CN109520170B (en)

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CN110243101A (en) * 2019-06-28 2019-09-17 中原工学院 A kind of accumulating type high-efficiency air cooling heat pump unit
CN112963979A (en) * 2021-03-14 2021-06-15 北京工业大学 Overlapping heat pump system capable of realizing work cycle conversion
CN113847708B (en) * 2021-08-31 2023-04-25 青岛海尔空调电子有限公司 Defrosting control method for air conditioner outdoor unit and air conditioner

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN202835900U (en) * 2012-09-26 2013-03-27 堃霖冷冻机械(上海)有限公司 Energy-efficient flooded type air-cooled heat pump unit
CN204648783U (en) * 2015-05-11 2015-09-16 浙江商业职业技术学院 With the hot fluorine defrosting device of heat exchange gas-liquid separator
CN106274372A (en) * 2016-11-14 2017-01-04 吉林大学 There is the heat-pump-type air conditioning for automobiles of battery thermal management function
CN106595151A (en) * 2016-12-30 2017-04-26 中原工学院 Three-stage combined type fast defrosting system of refrigeration device with intelligent control
WO2017193857A1 (en) * 2016-05-10 2017-11-16 比亚迪股份有限公司 Heat pump air-conditioning system and electric vehicle

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN202835900U (en) * 2012-09-26 2013-03-27 堃霖冷冻机械(上海)有限公司 Energy-efficient flooded type air-cooled heat pump unit
CN204648783U (en) * 2015-05-11 2015-09-16 浙江商业职业技术学院 With the hot fluorine defrosting device of heat exchange gas-liquid separator
WO2017193857A1 (en) * 2016-05-10 2017-11-16 比亚迪股份有限公司 Heat pump air-conditioning system and electric vehicle
CN106274372A (en) * 2016-11-14 2017-01-04 吉林大学 There is the heat-pump-type air conditioning for automobiles of battery thermal management function
CN106595151A (en) * 2016-12-30 2017-04-26 中原工学院 Three-stage combined type fast defrosting system of refrigeration device with intelligent control

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