CN109579356B - Temperature control multi-online heat pump system with heat recovery function and control method - Google Patents
Temperature control multi-online heat pump system with heat recovery function and control method Download PDFInfo
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- CN109579356B CN109579356B CN201811573057.5A CN201811573057A CN109579356B CN 109579356 B CN109579356 B CN 109579356B CN 201811573057 A CN201811573057 A CN 201811573057A CN 109579356 B CN109579356 B CN 109579356B
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- 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]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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Abstract
The invention provides a temperature control multi-online heat pump system with a heat recovery function and a control method thereof, wherein the temperature control multi-online heat pump system comprises a multi-online heat pump refrigeration system, a water tank, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve, a sixth electromagnetic valve, an electric control box and a first electronic expansion valve.
Description
Technical Field
The invention relates to the technical field of heat pump systems, in particular to a temperature control multi-online heat pump system with a heat recovery function and a control method.
Background
The multi-split heat pump system is widely used by people due to a flexible control method and a simple installation mode, but when the multi-split heat pump system is independently refrigerated, the heating quantity in the whole process is directly discharged to the outside through an outdoor unit arranged outdoors, so that the energy consumption of an outdoor fan is increased, and the heat generated by refrigeration is directly discharged to cause energy waste, in addition, the use range of a compressor is limited due to the high temperature of an electric control module of the multi-split system, most electric control modules of the multi-split system are cooled by the fan or a refrigerant to cool the modules at present, the mode is to transfer the heat into the system, and the superheat degree of the compressor in a gas-liquid separator is insufficient, the supercooling degree of the multi-split system is generally supercooled by an outdoor unit condenser, more condenser area is wasted to increase the supercooling degree, more cost is caused to the outdoor unit, and in addition, if the temperature of the return gas of the compressor is lower under the low temperature condition, the liquid return, the common method is to electrically heat the compressor, which not only wastes energy, but also causes the problems of low energy efficiency of the heat pump system, poor refrigeration effect and the like.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a temperature control multi-online heat pump system with a heat recovery function and a control method.
In order to achieve the purpose, the temperature control multi-split heat pump system with the heat recovery function comprises an evaporator, a condenser, a first variable frequency compressor, a second variable frequency compressor, a four-way valve, a multi-split indoor unit, an outdoor heat exchanger, a subcooler and a gas-liquid separator, wherein a first flow path and a second flow path which can exchange heat are arranged in the evaporator; the four-way valve comprises A, B, C, D four interfaces, the subcooler comprises E, F, G, H four interfaces, the output end of the second variable frequency compressor and one end of the outdoor heat exchanger are respectively communicated with an interface A and an interface B of the four-way valve, the other end of the outdoor heat exchanger and one end of the multi-connected indoor unit are respectively communicated with an interface E and an interface F of the subcooler, an interface D and an interface C of the four-way valve are respectively communicated with the other end of the multi-connected indoor unit and the gas-liquid separator, the gas-liquid separator is communicated with the input end of the second variable frequency compressor, the four-way valve further comprises a water tank, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve, a sixth electromagnetic valve, an electric control box and a first electronic expansion valve, wherein a first heat exchange tube is arranged in the electric control box, and two ends of the first heat exchange tube respectively, the outside of the water tank is respectively connected with an output port and an input port of the water tank through a preset second heat exchange tube, the second heat exchange tube circularly penetrates through the condenser, and two ends of the first electromagnetic valve are respectively communicated with an output end of the second variable frequency compressor and a connector A of the four-way valve; the components form a heat pump heat recovery module and an auxiliary heat exchange module of the system;
-the constituent connections of the heat pump heat recovery module: the output end of the first variable frequency compressor is communicated with one end of the condenser, two ends of a first flow path of the evaporator are respectively communicated with the input end of the first variable frequency compressor and the condenser, two ends of a second flow path of the evaporator are respectively communicated with a third electromagnetic valve and a second electromagnetic valve, the second electromagnetic valve is communicated with the output end of the second variable frequency compressor, and the third electromagnetic valve is communicated with an interface A of the four-way valve;
-the constituent connections of the auxiliary heat exchange modules: the fourth electromagnetic valve is arranged between the third electromagnetic valve and a connector A of the four-way valve, two ends of the first electronic expansion valve are respectively communicated with the third electromagnetic valve and a connector H of the subcooler, two ends of the electric control box are respectively communicated with a connector G of the subcooler and the gas-liquid separator, two ends of the sixth electromagnetic valve are respectively communicated with the third electromagnetic valve and the electric control box, the fifth electromagnetic valve is respectively communicated with the connector A of the four-way valve and the electric control box, and the gas-liquid separator is communicated with the fifth electromagnetic valve.
And one end of the oil separator is communicated with the output port of the second variable-frequency compressor, and the other end of the oil separator is respectively communicated with the first electromagnetic valve and the second electromagnetic valve.
Further, a second electronic expansion valve is arranged between the condenser and the evaporator.
Further, a third electronic expansion valve is arranged between the interface E of the subcooler and the outdoor heat exchanger.
Furthermore, a main low-pressure sensor is arranged between the input end of the second variable-frequency compressor and the gas-liquid separator.
Furthermore, the water temperature monitoring device also comprises a water temperature detector which is arranged in the water tank and used for monitoring the water temperature in real time, an electric control temperature detector which is arranged inside the electric control box and used for monitoring the temperature of elements inside the electric control box in real time, and a gas-liquid temperature detector which is arranged inside the gas-liquid separator and used for monitoring the temperature inside the gas-liquid separator in real time.
A control method of a temperature control multi-online heat pump system with a heat recovery function is characterized in that a water temperature detector is defined to monitor water temperature in real time to be real-time temperature T1, the required water temperature is set to be set temperature T1s, an electric control temperature detector monitors the internal temperature of an electric control box in real time to be real-time temperature T2, the internal temperature of the controlled electric control box is set to be T2s, a gas-liquid temperature detector monitors the internal temperature of a gas-liquid separator in real time to be real-time temperature T3, a corresponding low-pressure temperature at a main low-pressure sensor is Tpe, and the system correspondingly starts or closes a first variable-frequency compressor according to the comparison between the real-time temperature T1 and the set temperature T1s so; according to the comparison between the real-time temperature T2 and the set temperature T2s and the comparison between the real-time temperature T3 and the low-pressure temperature Tpe, the opening and closing of a fourth electromagnetic valve, a fifth electromagnetic valve and a sixth electromagnetic valve in the auxiliary heat exchange module are correspondingly controlled, and the opening degree of the first electronic expansion valve is adjusted;
if the set temperature T1s is greater than the real-time temperature T1, closing the first electromagnetic valve, opening the second electromagnetic valve and the third electromagnetic valve, starting the first variable frequency compressor by the system, starting the heat pump heat recovery module to perform heating work until the set temperature T1s is less than or equal to the real-time temperature T1, closing the first electromagnetic valve, opening the second electromagnetic valve and the third electromagnetic valve, stopping starting the first variable frequency compressor by the system, and stopping the heat pump heat recovery module to perform heating work;
if the real-time temperature T2 is greater than the set temperature T2s plus the Y value, closing the first electromagnetic valve and the fourth electromagnetic valve, opening the second electromagnetic valve and the third electromagnetic valve, and adjusting the opening degree of the first electronic expansion valve; opening the sixth electromagnetic valve until the real-time temperature T2 is less than or equal to a certain set temperature T2s plus X value;
if the difference value between the real-time temperature T3 and the low-pressure temperature Tpe is smaller than or equal to the set value Z, closing the first electromagnetic valve, the fourth electromagnetic valve and the fifth electromagnetic valve, and opening the second electromagnetic valve and the third electromagnetic valve; and when the difference value between the real-time temperature T3 and the low-pressure temperature Tpe is larger than a set value T, closing the first electromagnetic valve and the fourth electromagnetic valve, and opening the second electromagnetic valve, the third electromagnetic valve and the fifth electromagnetic valve.
Further, when the real-time temperature T2 is greater than the set temperature T2s plus Y value and less than or equal to the set temperature T2s plus X value, the set temperature T2s plus Y value gradually decreases with the increase of the set temperature T2s plus X value in the system operation, the valve body opening degree and the detection time of the first electronic expansion valve gradually decrease, when the X value and the Y value are both negative values, the fourth electromagnetic valve is closed, and the valve body opening degree of the first electronic expansion valve is a negative value.
Further, in the operation of the system, if the difference between the real-time temperature T3 and the low-pressure temperature Tpe is greater than the set value T and less than the set value Z, the opening and closing time of the valve body of the fifth electromagnetic valve is gradually and gradually changed along with the gradual increase of the set value T and the set value Z.
Further, during the operation of the system, the set temperature T1s is less than or equal to the real-time temperature T1, the real-time temperature T2 is less than or equal to a certain set temperature T2s plus X, and when the difference between the real-time temperature T3 and the preset temperature Tpe is greater than a certain set value T, the first solenoid valve and the fourth solenoid valve are closed, and the second solenoid valve, the third solenoid valve, the fifth solenoid valve and the sixth solenoid valve are opened.
The invention adopts the scheme, and has the beneficial effects that: according to the invention, the plurality of electromagnetic valves are arranged between the hot water system and the heat pump system to be alternately switched on and off to form different refrigerant flow paths, so that not only is the heat in the refrigeration of the heat pump effectively used for heating water to realize heat recovery, but also the high-temperature electronic control module is cooled by combining the multi-online heat recovery and the multi-online system through the related regulating valve, the supercooling degree of the heat pump system is increased, the superheat degree of a gas return port of a compressor is increased, the problems that the existing multi-online heat pump system is difficult to control and improve the supercooling degree of a liquid pipe and the superheat degree of the gas return port of the compressor are solved, and the problems that.
Drawings
FIG. 1 is a schematic structural diagram of the present invention.
Fig. 2 is a control flow chart of the water temperature detector of the present invention.
Fig. 3 is a control flowchart of the gas-liquid temperature detection portion of the present invention.
Fig. 4 is a control flow chart of the electric control temperature detection part of the present invention.
Wherein, 1-a first electromagnetic valve, 2-a second electromagnetic valve, 3-a third electromagnetic valve, 4-a fourth electromagnetic valve, 5-a fifth electromagnetic valve, 6-a gas-liquid separator, 61-a gas-liquid temperature detector, 7-a subcooler, 8-an electronic control box, 81-an electronic control temperature detector, 82-a first heat exchange tube, 9-a first electronic expansion valve, 10-a main low pressure sensor, 11-a first variable frequency compressor, 12-a sixth electromagnetic valve, 13-a water tank, 131-a water temperature detector, 132-a second heat exchange tube, 14-a water pump, 15-a condenser, 16-an evaporator, 17-a second electronic expansion valve, 18-an auxiliary high pressure sensor, 19-an auxiliary low pressure sensor, 20-a four-way valve, 21-an outdoor heat exchanger, 22-a third electronic expansion valve, 23-an indoor heat exchanger, 24-a second variable frequency compressor and 25-an oil separator.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious 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 derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1, in this embodiment, a temperature-controlled multi-split heat pump system with a heat recovery function mainly includes an evaporator 16, a condenser 15, a first inverter compressor 11, a second inverter compressor 24, a four-way valve 20, an oil separator 25, a multi-split indoor unit, an outdoor heat exchanger 21, a subcooler 7, a gas-liquid separator 6, a water tank 13, a first electromagnetic valve 1, a second electromagnetic valve 2, a third electromagnetic valve 3, a fourth electromagnetic valve 4, a fifth electromagnetic valve 5, a sixth electromagnetic valve 12, an electronic control box 8, and a first electronic expansion valve 9, wherein a first flow path and a second flow path capable of heat exchange are provided in the evaporator 16, the four-way valve 20 includes A, B, C, D four ports, the subcooler 7 includes E, F, G, H four ports, the multi-split indoor unit is connected in parallel by a plurality of indoor heat exchangers 23 (in this embodiment, the number of the indoor heat exchangers 23 is three, in addition, the number of the indoor heat exchangers 23 may be determined according to actual needs), specifically, the output end of the second inverter compressor 24 is communicated with the interface a of the four-way valve 20, the oil separator 25 is disposed between the second inverter compressor 24 and the four-way valve 20, that is, two ends of the oil separator 25 are respectively communicated with the output end of the second inverter compressor 24 and the interface a of the four-way valve 20, two ends of the outdoor heat exchanger 21 are respectively communicated with the interface B of the four-way valve 20 and one end of any indoor heat exchanger 23, wherein the subcooler 7 is disposed between the outdoor heat exchanger 21 and any indoor heat exchanger 23, the interface E and the interface F of the subcooler 7 are respectively communicated with one end of the outdoor heat exchanger 21 and one end of any indoor heat exchanger 23, further, a third electronic expansion valve 22 is disposed between the outdoor heat exchanger 21 and the interface E of the subcooler 7, and the opening degree of the electronic expansion valve is set to adjust the supercooling degree so as to reduce the The expansion valve is a common component in the field, and a skilled person can know the expansion valve through a related technical manual, and the principle of the expansion valve is not described herein in detail), the other end of any indoor heat exchanger 23 is communicated with a port D of the four-way valve 20, in addition, two ends of the gas-liquid separator 6 are respectively communicated with a port C of the four-way valve 20 and an input end of the second inverter compressor 24, further, a main low pressure sensor 10 is arranged between the gas-liquid separator 6 and the input end of the second inverter compressor 24, in addition, in this embodiment, both ends of the first solenoid valve 1 are respectively communicated with the output end of the second inverter compressor 24 and the interface A of the four-way valve 20 (since the oil separator 25 is between the second inverter compressor 24 and the four-way valve 20, that is, both ends of the first solenoid valve 1 are respectively communicated with the oil separator 25 and the interface A of the four-way valve 20), controlling the connection or blocking of the refrigerant passing through the output end of the second inverter compressor 24 to enter the interface A of the four-way valve 20 by the opening and closing of the first electromagnetic valve 1; in addition, in the present embodiment, the outside of the water tank 13 is connected to the output port and the input port of the water tank 13 through a preset second heat exchanging pipe 132, respectively, the water pump 14 is arranged at the output port of the water tank 13, wherein the second heat exchanging pipe 132 circulates through the condenser 15 a plurality of times, pumps the water in the water tank 13 to the second heat exchanging pipe 132 by the water pump 14, and flows back to the water tank 13 after being heated in the condenser 15 to obtain the required hot water, a first heat exchange pipe 82 is arranged in the electric control box 8, two ends of the first heat exchange pipe 82 respectively extend out of the electric control box 8 to be communicated with a connector G of the subcooler 7 and the gas-liquid separator 6, so that the refrigerant passing through the cooler 7 can exchange heat with the internal elements of the electronic control box 8 through the first heat exchange pipe 82, thereby reducing the temperature of the internal elements of the electric control box 8, and the components form a heat pump heat recovery module and an auxiliary heat exchange module of the system.
In this embodiment, the heat pump heat recovery module is composed of: the output end of the first inverter compressor 11 is communicated with one end of the condenser 15, two ends of a first flow path of the evaporator 16 are respectively communicated with the input end of the first inverter compressor 11 and the condenser 15, two ends of a second flow path of the evaporator 16 are respectively communicated with the third electromagnetic valve 3 and the second electromagnetic valve 2, wherein the second electromagnetic valve 2 is communicated with the output end of the second inverter compressor 24 (because the oil separator 25 is communicated with the output end of the second inverter compressor 24, namely, actually, the second electromagnetic valve 2 is communicated with the oil separator 25), and the third electromagnetic valve 3 is communicated with the interface A of the four-way valve 20; further, in the present embodiment, an auxiliary high pressure sensor 18 is provided between the output end of the first inverter compressor 11 and the condenser 15, a second electronic expansion valve 17 is provided between the first flow path of the evaporator 16 and the condenser 15, and an auxiliary low pressure sensor 19 is provided between the first flow path of the evaporator 16 and the input end of the first inverter compressor 11.
Further, in this embodiment, the connection of the auxiliary heat exchange module components is: two ends of the fourth electromagnetic valve 4 are respectively communicated with the third electromagnetic valve 3 and a connector A of the four-way valve 20, two ends of the first electronic expansion valve 9 are respectively communicated with the third electromagnetic valve 3 and a connector H of the subcooler 7, two ends of the electric control box 8 are respectively communicated with a connector G of the subcooler 7 and the gas-liquid separator 6 through the first heat exchange tube 82, two ends of the sixth electromagnetic valve 12 are respectively communicated with the third electromagnetic valve 3 and the electric control box 8, the fifth electromagnetic valve 5 is respectively communicated with the connector A of the four-way valve 20 and the electric control box 8, and the gas-liquid separator 6 is communicated with the fifth electromagnetic valve 5.
In addition, in this embodiment, the present invention further includes a water temperature detector 131 disposed in the water tank 13 and used for monitoring the water temperature in real time, an electronic control temperature detector 81 disposed in the electronic control box 8 and used for monitoring the temperature of the internal components of the electronic control box 8 in real time, and a gas-liquid temperature detector 61 disposed in the gas-liquid separator 6 and used for monitoring the temperature of the internal components of the gas-liquid separator 6 in real time, wherein the water temperature detected by the water temperature detector 131 in real time is defined as a real-time temperature T1, the required water temperature is a set temperature T1s, the electronic control temperature detector 81 monitors the internal temperature of the electronic control box 8 in real time as a real-time temperature T2, the controlled internal temperature of the electronic control box 8 is set as T2s, the gas-liquid temperature detector 61 monitors the internal temperature of the gas-liquid separator 6 in real time as a real-time temperature T3, the corresponding low-, the system correspondingly starts or stops the first inverter compressor 11 according to the comparison between the real-time temperature T1 and the set temperature T1s so as to start or stop the heat pump heat recovery module; according to the comparison between the real-time temperature T2 and the set temperature T2s and the comparison between the real-time temperature T3 and the low-pressure temperature Tpe, the opening and the closing of a fourth electromagnetic valve 4, a fifth electromagnetic valve 5 and a sixth electromagnetic valve 12 in the auxiliary heat exchange module are correspondingly controlled, and the opening degree of a first electronic expansion valve 9 is adjusted; in order to facilitate the understanding of the embodiment by the skilled person, the embodiment is described below with reference to specific examples:
as shown in fig. 1-4, the system starts to operate, wherein if the water temperature detector 131 detects that the set temperature T1s is greater than the real-time temperature T1, the system starts the first inverter compressor 11, and the heat pump heat recovery module starts to perform heating operation; closing the first electromagnetic valve 1, opening the second electromagnetic valve 2 and the third electromagnetic valve 3, at this time, the refrigerant with high temperature and high pressure passing through the output end of the first inverter compressor 11 passes through the auxiliary high pressure sensor 18 and flows to the condenser 15 for condensation and heat release, that is, the circulating water in the second heat exchange tube 132 in the condenser 15 is heated, the circulating water flows back to the water tank 13 through the water pump 14 to achieve the purpose of heating water, meanwhile, the refrigerant is condensed into liquid after passing through the condenser 15, throttled and depressurized by the second electronic expansion valve 17, flows to the first flow path of the evaporator 16 to be evaporated into gaseous refrigerant, passes through the auxiliary low pressure sensor 19 and flows to the input end of the first inverter compressor 11, so as to circulate, the refrigerant with high temperature and high pressure passing through the output end of the second inverter compressor 24 passes through the oil separator 25 and then flows to the second electromagnetic valve 2 and passes through the second flow path of the evaporator 16, at this time, the refrigerant with high temperature and high pressure exchanges, namely, the refrigerant in the first flow path of the evaporator 16 is used for absorbing the heat of the refrigerant passing through the second flow path of the evaporator 16, so that the refrigerant circulation quantity of the heat pump heat recovery module and the refrigerant superheat degree of the first inverter compressor 11 are improved, the compression ratio is reduced, the heating capacity and the energy efficiency ratio of the first inverter compressor 11 are further improved, and the refrigerant flows to the third electromagnetic valve 3 from the second flow path of the evaporator 16;
if the set temperature T1s is less than or equal to the real-time temperature T1, closing the first electromagnetic valve 1, opening the second electromagnetic valve 2 and the third electromagnetic valve 3, stopping starting the first inverter compressor 11 by the system, and stopping heating operation of the heat pump heat recovery module; the refrigerant with high temperature and high pressure at the output end of the second inverter compressor 24 flows to the second electromagnetic valve 2 through the oil separator 25 and flows to the third electromagnetic valve 3 through the second flow path of the evaporator 16 during the system operation, and then flows to the third electromagnetic valve 3 from the second flow path of the evaporator 16;
at this time, if the real-time temperature T2 of the electrically controlled temperature detector 81 is greater than the set temperature T2s plus the Y value, the first electromagnetic valve 1 and the fourth electromagnetic valve 4 are closed, the second electromagnetic valve 2 and the third electromagnetic valve 3 are opened, and the opening degree of the first electronic expansion valve 9 is adjusted; in the present embodiment, the value Y is 10, that is, when T2 is greater than T2s +10 ℃, at this time, because the temperature inside the electronic control box 8 is relatively high, the related throttling element is opened to allow the system refrigerant to flow into the electronic control box 8 for cooling, the first electromagnetic valve 1 and the fourth electromagnetic valve 4 are closed, the second electromagnetic valve 2 and the third electromagnetic valve 3 are opened, and the opening degree of the first electronic expansion valve 9 is adjusted, and at this time, the opening degree of the valve body of the first electronic expansion valve 9 is maximum; the refrigerant is divided into two paths after passing through the third electromagnetic valve 3, wherein one path of refrigerant is condensed and released heat through the outdoor heat exchanger 21, then flows through the third electronic expansion valve 22, then flows through the interface E and the interface F of the subcooler 7, then flows to any indoor heat exchanger 23 for evaporation and refrigeration, then flows into the input end of the second variable frequency compressor 24 through the main low pressure sensor 10 after passing through the interface D and the interface C of the four-way valve 20, passes through the gas-liquid separator 6, and flows into the electric control box 8 (through the first heat exchange tube 82) after passing through the first electronic expansion valve 9, flows to the interface H and the interface G of the subcooler 7 for supercooling so as to cool and radiate the inside of the electric; wherein, the refrigerant flows to the gas-liquid separator 6 after passing through the electric control box 8 and flows to the input end of the second variable-frequency compressor 24 through the main low-pressure sensor 10; further, when the real-time temperature T2 is greater than the set temperature T2s plus Y and less than or equal to the set temperature T2s plus X, the set temperature T2s plus Y gradually decreases with the decrease of the set temperature T2s plus X during the operation of the system, and the opening degree and the detection time of the valve body of the first electronic expansion valve 9 gradually decrease, specifically, in this embodiment, when T2s +5 ℃ < T2 ≤ T2s +10 ℃, the valve body of the first electronic expansion valve 9 is at this time +16P on the original basis, and is detected once every 20 seconds; when the temperature T2s +1 ℃ is more than T2 and less than or equal to T2s +5 ℃, the valve body of the first electronic expansion valve 9 is +8P on the original basis and is detected once in 10 seconds; when the temperature T2s-1 ℃ is more than T2 and less than or equal to T2s +1 ℃, the opening degree of the valve body of the first electronic expansion valve 9 is kept unchanged until the value X and the value Y are both negative values, the opening degree of the valve body of the first electronic expansion valve 9 is a negative value, in the embodiment, when the temperature T2s-4 ℃ is more than T2 and less than or equal to T2s-1 ℃, the valve body of the first electronic expansion valve 9 is-8P on the original basis and is detected once in 10 seconds; the system correspondingly adjusts the valve body opening of the first electronic expansion valve 9 and adjusts the detection time according to the real-time temperature T2 of the electronic control box 8 and the change between the preset temperature T2s and the difference value, so that the temperature inside the electronic control box 8 can be flexibly reduced by adjusting the valve body opening according to different temperatures inside the electronic control box 8; until the real-time temperature T2 is less than or equal to a certain set temperature T2s plus X, the fourth solenoid valve 4 is closed, the sixth solenoid valve 12 is opened, in this embodiment, when T2 is less than or equal to T2s-4 ℃, because the internal temperature of the electronic control box 8 is lower at this time, excessive refrigerant is not needed to reduce the internal temperature of the electronic control box 8, the flow rate of the refrigerant flowing into the electronic control box 8 can be reduced by increasing the refrigerant branch, so the fourth solenoid valve 4 is closed, the sixth solenoid valve 12 is opened, the refrigerant passing through the third solenoid valve 3 is divided into three parts, one part of the refrigerant passes through the outdoor heat exchanger 21, the third electronic expansion valve 22, the interface E and the interface F of the subcooler 7, the indoor heat exchanger 23, the four-way valve 20, the gas-liquid separator 6, the main low-pressure sensor 10 to the input end of the second inverter compressor 24, and the other part of the refrigerant passes through the first electronic expansion, The electronic control box 8, the gas-liquid separator 6 and the main low pressure sensor 10 are connected to the input end of the second variable frequency compressor 24, and the rest part of the refrigerant flows to the gas-liquid separator 6 through the sixth electromagnetic valve 12 in sequence and then passes through the main low pressure sensor 10 to be connected to the input end of the second variable frequency compressor 24.
Meanwhile, if the difference value between the real-time temperature T3 and the low-pressure temperature Tpe measured in the gas-liquid separator 6 is less than or equal to the set value Z, the first electromagnetic valve 1, the fourth electromagnetic valve 4 and the fifth electromagnetic valve 5 are closed, and the second electromagnetic valve 2 and the third electromagnetic valve 3 are opened; specifically, in this embodiment, the set value Z is-2, that is, when T3-TPe is less than or equal to-2 ℃, which indicates that the temperature of the refrigerant in the gas-liquid separator 6 is low, and the liquid return phenomenon is easily generated in the second inverter compressor 24, the second electromagnetic valve 2 and the third electromagnetic valve 3 are opened by closing the first electromagnetic valve 1, the fourth electromagnetic valve 4 and the fifth electromagnetic valve 5, so that the refrigerant flow rate through the gas-liquid separator 6 is increased by opening the refrigerant flow path, which is the same as the related electromagnetic valves and the electronic expansion valves in the relationship between T2 and T2s, so as to increase the temperature of the refrigerant in the gas-liquid separator 6, and when the difference between the real-time temperature T3 and the low-pressure temperature Tpe is greater than the set value T and less than the set value Z, the valve body opening and closing time of the fifth electromagnetic valve 5 is gradually increased along with the gradual increase of the set value T3 and the low-pressure temperature Tpe, specifically, when, closing the first electromagnetic valve 1 and the fourth electromagnetic valve 4, opening the second electromagnetic valve 2, the third electromagnetic valve 3 and the fifth electromagnetic valve 5, and opening the fifth electromagnetic valve 5 for 5 seconds and closing the fifth electromagnetic valve for 15 seconds; when the temperature is more than 2 ℃ and less than T3-TPe and less than 5 ℃, closing the first electromagnetic valve 1 and the fourth electromagnetic valve 4, opening the second electromagnetic valve 2, the third electromagnetic valve 3 and the fifth electromagnetic valve 5, and opening the fifth electromagnetic valve 5 for 10 seconds and closing the fifth electromagnetic valve for 10 seconds; when the difference value between the real-time temperature T3 and the low-pressure temperature Tpe is larger than a set value T, closing the first electromagnetic valve 1 and the fourth electromagnetic valve 4, and opening the second electromagnetic valve 2, the third electromagnetic valve 3 and the fifth electromagnetic valve 5; in this embodiment, when the temperature of 5 ℃ is less than T3-TPe, in order to prevent the temperature of the return air of the second inverter compressor 24 from being too high, at this time, the first electromagnetic valve 1 and the fourth electromagnetic valve 4 are closed, the second electromagnetic valve 2, the third electromagnetic valve 3 and the fifth electromagnetic valve 5 are opened, due to the opening of the fifth electromagnetic valve 5, the refrigerant passing through the interior of the electronic control box 8 is divided into two paths, wherein one path flows to the gas-liquid separator 6 and finally flows to the input end of the second inverter compressor 24, the other path flows to the fifth electromagnetic valve 5, then the refrigerant of the fifth electromagnetic valve 5 is divided into two portions, wherein one portion of the refrigerant flows to the gas-liquid separator 6, and the other portion of the refrigerant flows to the interface a of the four-way valve 20, the flow rate of the refrigerant flowing into the gas-liquid separator 6 is adjusted by the opening and closing of the fifth electromagnetic valve, the set temperature T1s is less than or equal to the real-time temperature T1, the real-time temperature T2 is less than or equal to a certain set temperature T2s plus X value, the difference value between the real-time temperature T3 and the preset temperature Tpe is more than a certain set value T, the first electromagnetic valve 1 and the fourth electromagnetic valve 4 are closed, the second electromagnetic valve 2, the third electromagnetic valve 3, the fifth electromagnetic valve 5 and the sixth electromagnetic valve 12 are opened, in the embodiment, when the T1 is more than or equal to the set value T1s, the T2 is more than or equal to T2s-4 ℃ and the temperature is less than T3-TPe, because the internal temperature of the electric control box 8 is lower and the supercooling degree of the gas-liquid separator 6 is higher, the first electromagnetic valve 1 and the fourth electromagnetic valve 4 are closed, the second electromagnetic valve 2, the third electromagnetic valve 3, the fifth electromagnetic valve 5, the sixth electromagnetic valve 12 and the first electronic expansion valve 9 are opened, so that the internal temperatures of the electric control box, the system throttling elements are adjusted in a segmented mode according to the temperature of the electric control box 8 and the temperature of the gas-liquid separator 6, so that the problems of poor system capacity, bias current, noise and the like caused by unreasonable opening degrees of the throttling elements such as an electronic expansion valve and the like are effectively solved on the premise of ensuring the reliable operation of the second variable-frequency compressor 24.
The above-described embodiments are merely preferred embodiments of the present invention, which is not intended to limit the present invention in any way. Those skilled in the art can make many changes, modifications, and equivalents to the embodiments of the invention without departing from the scope of the invention as set forth in the claims below. Therefore, equivalent variations made according to the idea of the present invention should be covered within the protection scope of the present invention without departing from the contents of the technical solution of the present invention.
Claims (4)
1. A control method of a temperature control multi-online heat pump system with a heat recovery function comprises a heat pump heat recovery module and an auxiliary heat exchange module:
the heat pump heat recovery module is connected with the following components: the output end of the first variable frequency compressor (11) is communicated with one end of a condenser (15), two ends of a first flow path of an evaporator (16) are respectively communicated with the input end of the first variable frequency compressor (11) and the condenser (15), two ends of a second flow path of the evaporator (16) are respectively communicated with a third electromagnetic valve (3) and a second electromagnetic valve (2), the second electromagnetic valve (2) is communicated with the output end of a second variable frequency compressor (24), and the third electromagnetic valve (3) is communicated with an interface A of a four-way valve (20);
the auxiliary heat exchange module is connected in a composition way: the fourth electromagnetic valve (4) is arranged between the third electromagnetic valve (3) and a connector A of the four-way valve (20), two ends of the first electronic expansion valve (9) are respectively communicated with the third electromagnetic valve (3) and a connector H of the subcooler (7), two ends of the electric control box (8) are respectively communicated with a connector G of the subcooler (7) and the gas-liquid separator (6), two ends of the sixth electromagnetic valve (12) are respectively communicated with the third electromagnetic valve (3) and the electric control box (8), the fifth electromagnetic valve (5) is respectively communicated with the connector A of the four-way valve (20) and the electric control box (8), and the gas-liquid separator (6) is communicated with the fifth electromagnetic valve (5);
comprises a water tank (13), a water temperature detector (131) arranged in the water tank (13) and used for monitoring water temperature in real time, an electric control temperature detector (81) arranged in the electric control box (8) and used for monitoring the temperature of internal elements of the electric control box (8) in real time, and a gas-liquid temperature detector (61) arranged in the gas-liquid separator (6) and used for monitoring the temperature of the internal elements of the gas-liquid separator (6) in real time, wherein the outside of the water tank (13) is respectively connected with an output port and an input port of the water tank (13) through a preset second heat exchange pipe (132), and the second heat exchange pipe (132) circularly penetrates through a condenser (,
the method is characterized in that: defining the water temperature detector (131) to monitor the water temperature in real time to be a real-time temperature T1, the required water temperature to be a set temperature T1s, the electric control temperature detector (81) to monitor the internal temperature of the electric control box (8) in real time to be a real-time temperature T2, the controlled internal temperature of the electric control box (8) to be T2s, the gas-liquid temperature detector (61) to monitor the internal temperature of the gas-liquid separator (6) in real time to be a real-time temperature T3, the corresponding low-pressure temperature at the main low-pressure sensor (10) to be Tpe, and the system correspondingly starts or closes the first variable-frequency compressor (11) according to the comparison between the real-time temperature T1 and the set temperature T1s so as to start or close the; according to the comparison between the real-time temperature T2 and the set temperature T2s and the comparison between the real-time temperature T3 and the low-pressure temperature Tpe, the opening and the closing of a fourth electromagnetic valve (4), a fifth electromagnetic valve (5) and a sixth electromagnetic valve (12) in the auxiliary heat exchange module are correspondingly controlled, and the opening degree of a first electronic expansion valve (9) is adjusted;
if the set temperature T1s is greater than the real-time temperature T1, closing the first electromagnetic valve (1), opening the second electromagnetic valve (2) and the third electromagnetic valve (3), starting the first variable frequency compressor (11) by the system, starting the heat pump heat recovery module to perform heating work until the set temperature T1s is less than or equal to the real-time temperature T1, closing the first electromagnetic valve (1), opening the second electromagnetic valve (2) and the third electromagnetic valve (3), stopping starting the first variable frequency compressor (11) by the system, and stopping the heat pump heat recovery module to perform heating work;
if the difference value between the real-time temperature T2 and the set temperature T2s is larger than the set Y value, closing the first electromagnetic valve (1) and the fourth electromagnetic valve (4), opening the second electromagnetic valve (2) and the third electromagnetic valve (3), and adjusting the opening degree of the first electronic expansion valve (9); opening the sixth electromagnetic valve (12) until the difference value between the real-time temperature T2 and the set temperature T2s is less than or equal to the set X value;
if the difference value between the real-time temperature T3 and the low-pressure temperature Tpe is smaller than or equal to the set Z value, closing the first electromagnetic valve (1), the fourth electromagnetic valve (4) and the fifth electromagnetic valve (5), and opening the second electromagnetic valve (2) and the third electromagnetic valve (3); when the difference value between the real-time temperature T3 and the low-pressure temperature Tpe is larger than a set value T, the first electromagnetic valve (1) and the fourth electromagnetic valve (4) are closed, and the second electromagnetic valve (2), the third electromagnetic valve (3) and the fifth electromagnetic valve (5) are opened; the Y value, the X value, the Z value and the set value T are changed set values, the X value is larger than the Y value, and the set value T is smaller than the Z value.
2. The method for controlling the temperature-controlled multi-split heat pump system with the heat recovery function as claimed in claim 1, wherein: when the difference value between the real-time temperature T2 and the set temperature T2s is larger than the set Y value and smaller than or equal to the set X value, if the sum of the set temperature T2s and the set X value is gradually reduced and the sum of the set temperature T2s and the set Y value is gradually reduced during the system operation, the valve body opening degree and the detection time of the first electronic expansion valve (9) are gradually reduced, and when the X value and the Y value are both set to be negative values, the fourth electromagnetic valve (4) is closed, and the valve body opening degree of the first electronic expansion valve (9) is a negative value.
3. The method for controlling the temperature-controlled multi-split heat pump system with the heat recovery function as claimed in claim 1, wherein: when the difference value between the real-time temperature T3 and the low-pressure temperature Tpe is larger than a set value T and smaller than a set value Z during system operation, if the set value T and the set value Z are gradually increased, the opening and closing time of the valve body of the fifth electromagnetic valve (5) is gradually and gradually changed, and the set value T is a changed set value.
4. The method for controlling the temperature-controlled multi-split heat pump system with the heat recovery function as claimed in claim 1, wherein: during system operation, if the set temperature T1s is less than or equal to the real-time temperature T1, the difference between the real-time temperature T2 and the set temperature T2s is less than or equal to the set X value, and the difference between the real-time temperature T3 and the preset temperature Tpe is greater than the set T value, the first electromagnetic valve (1) and the fourth electromagnetic valve (4) are closed, and the second electromagnetic valve (2), the third electromagnetic valve (3), the fifth electromagnetic valve (5) and the sixth electromagnetic valve (12) are opened.
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| CN111442578A (en) * | 2020-04-02 | 2020-07-24 | 北京力方圆制冷设备有限公司 | Refrigeration cycle system and refrigeration method |
| CN111503816B (en) * | 2020-04-29 | 2021-10-26 | 广东美的制冷设备有限公司 | Defrosting sound suppression method, storage medium, suppression device and air conditioner |
| CN112346493B (en) * | 2020-10-29 | 2021-11-09 | 北京京仪自动化装备技术有限公司 | Temperature control equipment and method |
| CN114440489B (en) * | 2020-12-28 | 2023-11-07 | 中科广能能源研究院(重庆)有限公司 | Air conditioning system of gas heat pump multi-unit and control method thereof |
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| CN102062495A (en) * | 2010-09-09 | 2011-05-18 | 宁波奥克斯电气有限公司 | Direct current variable frequency multifunctional air conditioning system and control method thereof |
| CN202581678U (en) * | 2012-03-28 | 2012-12-05 | Tcl空调器(中山)有限公司 | Multi-couple unit system with heat recovery function |
| CN102679482B (en) * | 2012-05-25 | 2014-09-17 | 宁波奥克斯空调有限公司 | Heat recovery multiplex system based on variable-frequency air conditioner and control method thereof |
| CN203595314U (en) * | 2013-07-03 | 2014-05-14 | Tcl空调器(中山)有限公司 | Multi-online system |
| CN203785307U (en) * | 2013-12-03 | 2014-08-20 | 李东灿 | Ultralow-temperature air energy double-compressor heat pump |
| US10724776B2 (en) * | 2016-04-21 | 2020-07-28 | Mitsubishi Electric Corporation | Exhaust heat recovery type of air-conditioning apparatus |
| CN206269424U (en) * | 2016-10-26 | 2017-06-20 | 广东高而美制冷设备有限公司 | It is a kind of can recuperation of heat purging system |
| CN108088008B (en) * | 2017-12-12 | 2024-02-02 | 珠海格力电器股份有限公司 | Multi-split air conditioner and heat recovery system thereof |
| CN108731187B (en) * | 2018-06-20 | 2020-05-08 | 广东美的暖通设备有限公司 | Three-pipe heat recovery multi-split air conditioner system and control method thereof |
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