WO2020082735A1 - 热泵系统及空调器 - Google Patents

热泵系统及空调器 Download PDF

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Publication number
WO2020082735A1
WO2020082735A1 PCT/CN2019/089266 CN2019089266W WO2020082735A1 WO 2020082735 A1 WO2020082735 A1 WO 2020082735A1 CN 2019089266 W CN2019089266 W CN 2019089266W WO 2020082735 A1 WO2020082735 A1 WO 2020082735A1
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WO
WIPO (PCT)
Prior art keywords
valve
heat exchanger
heating
pump system
valve port
Prior art date
Application number
PCT/CN2019/089266
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English (en)
French (fr)
Inventor
罗彬�
杨坤
占磊
刘树清
谭志军
Original Assignee
合肥美的暖通设备有限公司
广东美的暖通设备有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 合肥美的暖通设备有限公司, 广东美的暖通设备有限公司 filed Critical 合肥美的暖通设备有限公司
Priority to US16/618,158 priority Critical patent/US20210364206A1/en
Priority to EP19801655.2A priority patent/EP3680578B1/en
Publication of WO2020082735A1 publication Critical patent/WO2020082735A1/zh

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Classifications

    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/008—Refrigerant heaters
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F25B2347/023—Set point defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle

Definitions

  • the present application relates to the technical field of air conditioning, and in particular to a heat pump system and an air conditioner using the heat pump system.
  • the refrigerant absorbs heat from the outdoor side through the outdoor heat exchanger, and then increases the pressure and temperature through the compressor, and discharges the heat from the outdoor side to the indoor to achieve the heating effect.
  • the refrigerant in the outdoor heat exchanger needs to absorb the heat of the outdoor air, which needs to be lower than the temperature of the outdoor air, which will cause the outdoor heat exchanger to frost in the heating mode. After defrosting, defrosting is required to ensure the safe and effective operation of the system.
  • the existing heat pump system needs to absorb heat from the indoor side during the defrosting process, resulting in a decrease in indoor temperature, the indoor unit cannot heat normally, and when the outdoor unit resumes the heating mode, it takes a period of time to switch and start the compressor gradually Heating the refrigerant system reduces the energy efficiency of the operation.
  • the refrigerant oil discharged from the compressor is highly soluble in liquid refrigerant.
  • the concentration of the refrigerant oil in the compressor is late The late rise is less than the safe concentration.
  • the existing heat pump system needs to operate at low frequency for a long time to vaporize the liquid refrigerant in the compressor, reduce the content of refrigerant in the frozen oil returned by the oil separator, and increase the content of refrigerant oil in the compressor to safety After the concentration, the normal operation can be carried out. This process lasts a long time. Even after the indoor unit is turned on for more than ten minutes, there is still no hot air blowing out, and the starting speed is slow.
  • the main purpose of the present application is to provide a heat pump system, which aims to enable the heat pump system to achieve non-stop defrosting while ensuring the normal heating of the indoor unit, and to improve the operation energy efficiency and indoor heating comfort.
  • it provides heat for the low-temperature gas-liquid mixed refrigerant discharged from the compressor, evaporates the liquid refrigerant contained in the frozen oil discharged by the compressor as soon as possible, and quickly reduces the refrigerant in the frozen oil returned by the oil separator
  • the content makes the concentration of refrigeration oil in the compressor quickly increase to a safe level, thereby reducing the time required for the compressor to start to high-frequency operation and speeding up the system start-up speed.
  • the heat pump system proposed in this application includes a compressor assembly, an outdoor heat exchanger, and an indoor heat exchanger.
  • the heat pump system also includes: a heat storage device and a switching device; the compressor assembly, the switching device , An outdoor heat exchanger and an indoor heat exchanger are connected in sequence to form a refrigeration circuit, and the heating heat storage device and the switching device are arranged in series;
  • the heat pump system has a first heating mode, a second heating mode, and a defrosting mode under the switching of the switching device, wherein in the first heating mode, the refrigerant discharged from the compressor assembly passes The switching device and the heating heat storage device sequentially enter the indoor heat exchanger and the outdoor heat exchanger, and flow back to the compressor assembly; in the second heating mode, the compressor assembly discharges The refrigerant enters the indoor heat exchanger and the outdoor heat exchanger in sequence through the switching device, and flows back to the compressor assembly; in the defrosting mode, the refrigerant discharged from the compressor assembly sequentially passes through the switching device After entering the indoor heat exchanger and the outdoor heat exchanger, the refrigerant flowing out of the outdoor heat exchanger flows back to the compressor assembly through the heating heat storage device.
  • the switching device includes a first four-way valve and a second four-way valve arranged in series, the first four-way valve has first to fourth valve ports, and the second four-way valve has fifth to fourth Eight valve ports, the compressor assembly communicates with the first valve port, the outdoor heat exchanger communicates with the eighth valve port, and one end of the heated heat storage device communicates with the fourth valve port, The other end communicates with the fifth valve port, the indoor heat exchanger communicates with the second valve port and the sixth valve port, and the third valve port and the seventh valve port are both connected to the compressor The suction end is connected;
  • the first valve port and the fourth valve port of the first four-way valve are conducted, and the fifth valve port, the sixth valve port, and the seventh valve port of the second four-way valve
  • the valve port and the eighth valve port are conducting respectively;
  • the first and second valve ports of the first four-way valve are conducted, and the seventh and eighth valve ports of the second four-way valve are conducted;
  • the first and second valve ports, the third and fourth valve ports of the first four-way valve respectively conduct, and the fifth valve of the second four-way valve Port and the eighth valve port conduct.
  • the switching device further includes a first solenoid valve, and the first solenoid valve is disposed between the sixth valve port and the indoor heat exchanger.
  • the heat pump system further includes a first one-way valve, and the first one-way valve is connected between the outdoor heat exchanger and the heating heat storage device.
  • the heat pump system further includes a throttling device, one end of the throttling device communicates with the heating heat storage device, and the other end communicates with the fifth valve port and the first check valve.
  • the heat pump system further includes a second one-way valve, and the second one-way valve is connected between the second valve port and the indoor heat exchanger.
  • the heat pump system also has a cooling mode under the switching of the switching device.
  • the cooling mode the first valve port and the fourth valve port of the first four-way valve are conducted, and the first The fifth and eighth valve ports, the sixth and seventh valve ports of the two- and four-way valves are respectively conducted.
  • the heating heat storage device includes a second solenoid valve and a heat exchanger, and the heat exchanger is connected in series with the second solenoid valve to communicate with the switching device;
  • the heating heat storage device further includes a heating component and / or a heat storage component, and the heating component and / or the heat storage component is disposed on an outer wall of the heat exchanger.
  • the heating component is an exogenous heater
  • the heat storage component is a heat accumulator.
  • the present application also proposes an air conditioner including a heat pump system
  • Heat pump system including compressor assembly, outdoor heat exchanger and indoor heat exchanger, the heat pump system also includes: heating heat storage device and switching device; the compressor assembly, switching device, outdoor heat exchanger and indoor heat exchange The devices are connected in sequence to form a refrigeration circuit, and the heating heat storage device and the switching device are arranged in series;
  • the heat pump system has a first heating mode, a second heating mode, and a defrosting mode under the switching of the switching device, wherein in the first heating mode, the refrigerant discharged from the compressor assembly passes The switching device and the heating heat storage device sequentially enter the indoor heat exchanger and the outdoor heat exchanger, and flow back to the compressor assembly; in the second heating mode, the compressor assembly discharges The refrigerant enters the indoor heat exchanger and the outdoor heat exchanger in sequence through the switching device, and flows back to the compressor assembly; in the defrosting mode, the refrigerant discharged from the compressor assembly sequentially passes through the switching device After entering the indoor heat exchanger and the outdoor heat exchanger, the refrigerant flowing out of the outdoor heat exchanger flows back to the compressor assembly through the heating heat storage device.
  • the heat pump system in the first heating mode, the refrigerant is discharged from the compressor assembly, enters the indoor heat exchanger and the outdoor heat exchanger in sequence through the switching device and the heat storage device, and flows back to the compressor assembly.
  • the refrigerant is heated by the heating and heat storage device, which improves the energy efficiency of the entire heat pump system and speeds up the startup;
  • the heat pump system can be between the first heating mode and the second heating mode when it starts up and runs normally Switching, in the second heating mode, the refrigerant is discharged from the compressor assembly and then enters the indoor heat exchanger and outdoor heat exchanger in sequence through the switching device, and flows back to the compressor assembly, in this process to ensure the normal heating of the heat pump system heat;
  • the high-temperature and high-pressure refrigerant discharged from the compressor assembly is partially condensed in the indoor heat exchanger, and then flows to the outdoor heat exchanger to defrost the outdoor heat exchanger.
  • the refrigerant flowing from the outdoor heat exchanger absorbs heat through the heat storage device to evaporate and flow back to the compressor assembly, thereby achieving non-stop heating and defrosting, and at the same time keeping the indoor temperature from falling, improving the energy efficiency of the heat pump system Heating comfort.
  • the heat pump system proposed in this application uses a switching device to switch the refrigerant discharged from the compressor assembly in different modes, and uses a heat storage device to enable the heat pump system to keep heating and defrosting while heating, improving the energy efficiency of the system. And heating comfort.
  • 1 is a schematic diagram of the refrigerant flow direction of the heat pump system of the present application in the first heating mode
  • FIG. 2 is a schematic diagram of the refrigerant flow direction of the heat pump system of the present application in the second heating mode
  • FIG. 3 is a schematic diagram of the refrigerant flow direction of the heat pump system of the present application in the defrosting mode
  • FIG. 4 is a schematic diagram of the refrigerant flow direction of the heat pump system of the present application in the cooling mode.
  • first, second, etc. in this application are for descriptive purposes only, and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of indicated technical features.
  • the features defined with “first” and “second” may include at least one of the features either explicitly or implicitly.
  • the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary people in the art to achieve, when the combination of technical solutions conflicts with each other or cannot be realized, it should be considered that the combination of such technical solutions does not exist , Nor within the scope of protection required by this application.
  • This application proposes a heat pump system 100.
  • the heat pump system 100 includes a compressor assembly 10, an outdoor heat exchanger 20, an indoor heat exchanger 30, a heating heat storage device 50, and a switching device 40.
  • the switching device 40, the outdoor heat exchanger 20, and the indoor heat exchanger 30 are sequentially connected to form a refrigeration circuit, and the heating heat storage device 50 and the switching device 40 are provided in series.
  • the heat pump system 100 has a first heating mode, a second heating mode, and a defrosting mode under the switching of the switching device 40, wherein in the first heating mode, the refrigerant discharged from the compressor assembly 10 passes through the switching device 40 and is heated
  • the heat storage device 50 enters the indoor heat exchanger 30 and the outdoor heat exchanger 20 in sequence, and flows back to the compressor assembly 10; in the second heating mode, the refrigerant discharged from the compressor assembly 10 enters the indoor exchange through the switching device 40 in turn
  • the heater 30 and the outdoor heat exchanger 20 flow back to the compressor assembly 10; in the defrosting mode, the refrigerant discharged from the compressor assembly 10 enters the indoor heat exchanger 30 and the outdoor heat exchanger 20 in sequence through the switching device 40,
  • the refrigerant flowing out of the outdoor heat exchanger 20 flows back to the compressor assembly 10 through the heating heat storage device 50.
  • the compressor assembly 10 includes a compressor 11 and a liquid separator 12 arranged in series.
  • the compressor assembly 10 has a steam discharge port 111 and a liquid return port 112.
  • the steam discharge port 111 is provided in the compressor 11 and the liquid return port 112 is provided.
  • the steam outlet 111 of the compressor 11 is connected to the switching device 40 for discharging high-temperature and high-pressure superheated steam.
  • the heat pump system 100 has a first heating mode, a second heating mode, and a defrosting mode under the switching of the switching device 40. It can be understood that when the heat pump system 100 is in the first heating mode, the refrigerant is discharged from the exhaust port 111 of the compressor 11 through the switching device 40 and the heating heat storage device 50 into the indoor heat exchanger 30 and the outdoor heat exchanger 20 in sequence , And flows back to the liquid separator 12 from the liquid return port 112, and flows into the compressor 11 again. In this process, the refrigerant is further heated by the heat storage device 50, so that after the indoor heat exchanger 30 releases heat, the temperature of the refrigerant is still relatively high. When the heat is absorbed at the outdoor heat exchanger 20, the outdoor heat exchanger 20 does not A frosting phenomenon occurs, thereby improving the operational energy efficiency of the entire heat pump system 100 and accelerating the startup speed.
  • the second heating mode is the normal heating mode.
  • the heat pump system 100 is in the second heating mode, the refrigerant The steam exhaust port 111 is discharged into the indoor heat exchanger 30 and the outdoor heat exchanger 20 in sequence through the switching device 40, and flows back to the liquid separator 12 through the liquid return port 112, and flows into the compressor 11 again.
  • the high-temperature and high-pressure refrigerant discharged from the exhaust port 111 of the compressor 11 releases heat in the indoor heat exchanger 30 to heat up the indoor environment and absorb heat at the outdoor heat exchanger 20 to achieve normal purity Heating mode.
  • the heat pump system 100 may also switch between the first heating mode and the second heating mode.
  • the refrigerant When the heat pump system 100 performs defrosting in the defrosting mode, the refrigerant is discharged from the exhaust port 111 of the compressor 11 and partially condensed in the indoor heat exchanger 30, and then flows to the outdoor heat exchanger 20 to treat the outdoor heat exchanger 20. After defrosting, the refrigerant flowing from the outdoor heat exchanger 20 absorbs heat through the heat storage device 40 to evaporate, flows back to the liquid separator 12 from the liquid return port 112, and flows into the compressor 11 again, thereby realizing non-stop heating and defrosting During the defrosting period, the indoor temperature is not decreased, which improves the energy efficiency and heating comfort of the heat pump system 100.
  • the heat pump system 100 proposed by the present application uses a switching device 40 to switch the refrigerant discharged from the compressor assembly 10 in different modes, and uses a heat storage device 40 to enable the heat pump system 100 to continuously heat and defrost while heating. To improve the energy efficiency and heating comfort of the system.
  • the switching device 40 includes a first four-way valve 41 and a second four-way valve 42 arranged in series.
  • the first four-way valve 41 has a first valve port A1, a second valve port B1, a third valve port C1, and a fourth valve port D1;
  • the second four-way valve 42 has a fifth valve port A2, a sixth valve port B2, The seventh valve port C2 and the eighth valve port D2.
  • the compressor assembly 10 communicates with the first valve port A1
  • the outdoor heat exchanger 20 communicates with the eighth valve port D2
  • one end of the heating heat storage device 50 communicates with the fourth valve port D1
  • the other end communicates with the fifth valve port A2 communicates
  • the indoor heat exchanger 30 communicates with the second valve port B1 and the sixth valve port B2
  • the third valve port C1 and the seventh valve port C2 both communicate with the suction end of the compressor assembly 10.
  • the heat pump system 100 of the present application switches the ports of the first four-way valve 41 and the second four-way valve 42 to switch between different modes, and uses the heat storage device 50 to cooperate with the different modes, thereby
  • the heat pump system 100 realizes functions such as rapid start-up, normal heating and non-stop heating and defrosting, etc., and improves the energy efficiency and heating comfort of the system.
  • the first valve port A1 and the fourth valve port D1 of the first four-way valve 41 conduct, and the fifth valve port A2 of the second four-way valve 42 and The sixth valve port B2, the seventh valve port C2, and the eighth valve port D2 are respectively conducted.
  • the refrigerant is discharged from the exhaust port 111 of the compressor 11 through the first valve port A1 and the fourth valve port D1 of the first four-way valve 41, is further heated by the heating heat storage device 50, and passes through the fifth of the second four-way valve 42. After the valve port A2 and the sixth valve port B2, they enter the indoor heat exchanger 30 to radiate heat. At this time, the temperature of the refrigerant is still relatively high.
  • the second four-way valve 42 After absorbing heat at the outdoor heat exchanger 20, the second four-way valve 42 The eight valve port D2 and the seventh valve port C2 flow out, and return to the liquid separator 12 from the liquid return port 112, and flow into the compressor 11 again. After the higher temperature refrigerant absorbs heat at the outdoor heat exchanger 20, frost does not occur in the outdoor heat exchanger 20, thereby improving the operating energy efficiency of the entire heat pump system 100 and speeding up the startup.
  • the first valve port A1 and the second valve port B1 of the first four-way valve 41 are conducted, and the seventh valve port C2 and the eighth valve port D2 of the second four-way valve 42 Turn on.
  • the refrigerant is discharged from the exhaust port 111 of the compressor 11 through the first valve port A1 and the second valve port B1 of the first four-way valve 41, enters the indoor heat exchanger 30 to radiate heat, heats the indoor environment, and is replaced outdoors
  • the heat absorber 20 absorbs heat, and then flows out from the eighth port D2 and the seventh valve port C2 of the second four-way valve 42, and returns to the liquid separator 12 from the liquid return port 112, and flows into the compressor 11 again. Achieve normal pure heating mode.
  • the first valve port A1 and the second valve port B1, the third valve port C1 and the fourth valve port D1 of the first four-way valve 41 are respectively conducted, and the The fifth valve port A2 and the eighth valve port D2 are conducted.
  • the refrigerant is discharged from the exhaust port 111 of the compressor 11 through the first valve port A1 and the second valve port B1 of the first four-way valve 41, enters the indoor heat exchanger 30 to radiate heat, heats the indoor environment, and is replaced outdoors
  • the heat absorber 20 absorbs heat, and then flows out through the eighth port D2 and the fifth port A2 of the second four-way valve 42, absorbs heat through the heating heat storage device 40 and evaporates from the liquid return port 112 to the liquid separator 12 , Flows into the compressor 11 again.
  • the heat pump system 100 realizes non-stop heating and defrosting, and keeps the indoor temperature from falling during the defrosting period, which improves the energy efficiency and heating comfort of the heat pump system 100.
  • the heat pump system 100 also has a cooling mode under the switching of the switching device 40, that is, the normal cooling mode of the heat pump system 100.
  • the first valve port A1 and the fourth valve port D1 of the first four-way valve 41 conduct, and the fifth valve port A2 and the eighth valve port D2 of the second four-way valve 42 and the sixth
  • the valve port B2 and the seventh valve port C2 are respectively conducted.
  • the refrigerant is discharged from the exhaust port 111 of the compressor 11 through the first valve port A1 and the fourth valve port D1 of the first four-way valve 41, and flows through the heating heat storage device 40.
  • the high-pressure refrigerant partially absorbs or stores heat, and then flows into the outdoor heat exchanger 20 through the fifth valve port A2 and the eighth valve port D2 of the second four-way valve 42 to release heat, and absorbs heat in the indoor heat exchanger 30, In order to cool the indoor environment, it flows out from the sixth valve port B2 and the seventh valve port C2 of the second four-way valve 42, flows back to the liquid separator 12 from the liquid return port 112, and flows into the compressor 11 again.
  • the switching device 40 further includes a first solenoid valve 43, and the first solenoid valve 43 is provided between the sixth valve port B2 and the indoor heat exchanger 30. It can be understood that the setting of the first solenoid valve 43 is beneficial to the cooperation of the first solenoid valve 43 and the second four-way valve 42 when the switching device 40 switches between different modes, so as to smoothly realize the direct switching of different modes.
  • the heat pump system 100 further includes a throttle device 70 and a first check valve 60.
  • the first check valve 60 is connected to the outdoor heat exchanger 20 and the heating Between the heat storage devices 50, one end of the throttle device 70 communicates with the heating heat storage device 50, and the other end communicates with the fifth valve port A2 and the first check valve 60.
  • the throttle device 70 is an electronic expansion valve or a capillary tube.
  • the heat pump system 100 further includes a second one-way valve 80.
  • the second one-way valve 80 is connected to the second valve port B1 and the indoor heat exchanger 30. between.
  • the heat pump system 100 opens the throttle device 70 and the first solenoid valve 43, closes the first check valve 60 and the second check valve 80, and the first of the first four-way valve 41
  • the valve port A1 and the fourth valve port D1 connect the exhaust port 111 of the compressor 11 to the heating heat storage device 50, and the fifth valve port A2 and the sixth valve port B2 of the second four-way valve 42 heat the heating storage device 50 It communicates with the first solenoid valve 43 and the indoor heat exchanger 30.
  • the high-pressure gaseous refrigerant discharged from the exhaust port 111 of the compressor 11 is heated in the heating heat storage device 50 (or condenses and releases a part of heat to the heating heat storage device 50), and then is sent to the indoor heat exchanger 30 through the first solenoid valve 43 Heat release, the liquid refrigerant flowing out of the indoor heat exchanger 30 absorbs heat and evaporates into a gaseous refrigerant in the outdoor heat exchanger 20, flows out through the eighth valve port D2 and the seventh valve port C2 of the second four-way valve 42, and flows out The liquid return port 112 flows back to the liquid separator 12 and flows into the compressor 11 again.
  • the heat pump system 100 closes the throttle device 70, the first solenoid valve 43, and the first check valve 60, opens the second check valve 80, and the first port of the first four-way valve 41
  • the two-valve port B1 communicates the exhaust port 111 of the compressor 11 with the second check valve 80 and the indoor heat exchanger 30.
  • the high-pressure gaseous refrigerant discharged from the exhaust port 111 of the compressor 11 passes through the first four-way valve 41, the first The two one-way valve 80 flows to the indoor heat exchanger 30 to release heat, and heats up the indoor environment.
  • the high-pressure liquid refrigerant absorbs heat in the outdoor heat exchanger 20 and evaporates into a gaseous refrigerant, passing through the eighth port of the second four-way valve 42 D2 and the seventh valve port C2 flow out, and return to the liquid separator 12 through the liquid return port 112, and then flow into the compressor 11 again to realize the normal pure heating mode.
  • the heat pump system 100 opens the throttle device 70, the first check valve 60 and the second check valve 80, closes the first solenoid valve 43, and the first valve of the first four-way valve 41 and the second valve Port B1 connects the exhaust port 111 of the compressor 11 with the second check valve 80 and the indoor heat exchanger 30.
  • the high-pressure gaseous refrigerant discharged from the exhaust port 111 of the compressor 11 passes through the first four-way valve 41 and the second unit
  • the directional valve 80 flows to the indoor heat exchanger 30 to radiate heat, which heats up the indoor environment.
  • the refrigerant continues to condense and release heat in the outdoor heat exchanger 20, melting frost on the outdoor heat exchanger 20, and the generated liquid refrigerant passes through the first unidirectional
  • the valve 60 and the throttle device 70 flow through the heat storage device 40 to absorb heat and evaporate, and flow into the liquid return port 112 and flow back to the dispenser through the fourth valve port D1 and the third valve port C1 of the first four-way valve 41 12. It flows into the compressor 11 again, so that the heat pump system 100 realizes non-stop heating and defrosting, and keeps the indoor temperature from falling during the defrosting period, which improves the energy efficiency and heating comfort of the heat pump system 100.
  • the first flow path is from the outdoor heat exchanger 20 to the heating heat storage device 40 through the first check valve 60 and the throttle device 70;
  • the second flow path is from the outdoor heat exchanger 20 to the second four-way valve
  • the eighth valve port D2 and the fifth valve port A2 of 42 and the throttle device 70 flow into the heating heat storage device 40.
  • the two flow paths are affected by the pressure, and usually the refrigerant flows from the first flow path to the heating heat storage device 40.
  • the second four-way valve 42 temporarily fails.
  • the heat pump system 100 opens the throttle device 70 and the first check valve 60, closes the first check valve 60 and the second check valve 80, and the first valve port A1 and the first
  • the four-valve port D1 connects the exhaust port 111 of the compressor 11 to the heating heat storage device 50, and the fifth and eighth valve ports A2 and D2 of the second four-way valve 42 heat the thermal storage device 50 and the outdoor heat exchanger 20, the sixth valve port B2 and the seventh valve port C2 of the second four-way valve 42 communicate the indoor heat exchanger 30 and the liquid return port 112 of the liquid separator 12.
  • the high-pressure gas refrigerant discharged from the exhaust port 111 of the compressor 11 passes through the first four-way valve 41, the throttle device 70, and the second four-way valve 42 and then flows into the outdoor heat exchanger 20 to be condensed into a high-pressure liquid refrigerant and flows into the indoor heat exchange.
  • the throttling in the device 30 evaporates into a low-pressure gaseous refrigerant, flows out through the sixth valve port B2 and the seventh valve port C2 of the second four-way valve 42, flows back to the separator 12 from the liquid return port 112, and flows into the compressor 11 again To cool the indoor environment.
  • the heating heat storage device 50 includes a second solenoid valve, a heat exchanger 52 and a heating assembly 51.
  • the heating assembly 51 is disposed on the outer wall of the heat exchanger 52 and heat
  • the exchanger 52 connects the second solenoid valve in series with the switching device 40. It can be understood that the second solenoid valve is used to control the working state of the heat exchanger and the heating assembly 51.
  • the heating component 51 is an exogenous heater.
  • the exogenous heater may be an electric heating device or a gas heating device.
  • the heating component 51 is preferably electrically heated.
  • the electrical heating is attached to the outer wall of the heat exchanger 52, and the electric heating is controlled by a second solenoid valve to achieve heating of the outer wall of the heat exchanger 52.
  • the heat exchanger 52 can exchange heat.
  • the heat storage device 50 includes a second solenoid valve, a heat exchanger 52, and a heat storage component (not shown).
  • the heat storage component is disposed on the outer wall of the heat exchanger 52, and the heat exchanger 52 is connected in series
  • the solenoid valve communicates with the switching device 40.
  • the second solenoid valve is used to control the working state of the heat exchanger
  • the heat storage component may be a heat storage
  • the heat storage may use a heat storage material for heat exchange
  • the heat storage material may be a phase change Materials or sensible heat storage materials are not limited here.
  • the heat storage module preferably uses heat storage fins made of heat storage materials.
  • the heat storage fins are disposed on the outer wall of the heat exchanger 52.
  • the heat storage fins pass through the heat exchanger 52 for heat storage.
  • the heat stored in the heat storage fins is used to vaporize the liquid refrigerant when the lower temperature liquid refrigerant returns to the compressor, thereby reducing the content of refrigerant in the frozen oil returned by the liquid separator 12, and increasing the content of the refrigerant oil in the compressor to a safe concentration. Achieve normal operation, thereby reducing the time required for the compressor to start to high-frequency operation and speeding up the system startup speed.
  • the heating heat storage device 50 includes a second solenoid valve, a heat exchanger 52, a heating assembly 51 and a heat storage assembly (not shown), the heating assembly 51 and the heat storage
  • the heat components are arranged on the outer wall of the heat exchanger 52 at intervals, and the second electromagnetic valve connected in series with the heat exchanger 52 communicates with the switching device 40.
  • the second solenoid valve is used to control the working state of the heat exchanger and heating assembly 51.
  • the heating component 51 is an exogenous heater.
  • the exogenous heater may be an electric heating device or a gas heating device.
  • the heat storage component may be a heat accumulator.
  • the heat accumulator may use a heat storage material for heat exchange.
  • the thermal material may be a phase change material or a sensible heat storage material, which is not limited herein.
  • the heating component 51 is preferably electrically heated.
  • the electrical heating is attached to the outer wall of the heat exchanger 52, and the electric heating is controlled by a second solenoid valve to achieve heating of the outer wall of the heat exchanger 52.
  • the heat exchanger 52 can exchange heat.
  • the heat storage module preferably uses heat storage fins made of heat storage materials.
  • the heat storage fins are provided on the outer wall of the heat exchanger 52.
  • the heat storage fins also store heat through the heat exchanger 52; or when a refrigerant with a higher temperature exchanges heat through the heat exchanger 52, the heat storage fins also store heat through the heat exchanger 52.
  • the heat stored in the heat storage fins is used to vaporize the liquid refrigerant when the lower temperature liquid refrigerant returns to the compressor, thereby reducing the content of refrigerant in the frozen oil returned by the liquid separator 12, and increasing the content of the refrigerant oil in the compressor to a safe concentration. Normal operation is achieved, thereby reducing the time required for the compressor to start to high-frequency operation, and speeding up the system startup speed.
  • the present application also proposes an air conditioner including a heat pump system 100.
  • the specific structure of the heat pump system refers to the above embodiments. Since the control method of the heat pump system uses all the technical solutions of all the above embodiments, it has at least the above All the beneficial effects brought by the technical solutions of the embodiments will not be repeated here one by one.
  • the air conditioner of the present application includes a heat pump system 100.
  • the heat pump system 100 uses a switching device 40 to switch the refrigerant discharged from the compressor assembly 10 in different modes.
  • the heat storage system 50 is used in conjunction with the switching device 40 to make the heat pump system 100 in production. At the same time of heating, it can realize non-stop heating and defrosting, thereby improving the operation energy efficiency and heating comfort of the air conditioner.

Abstract

一种热泵系统(100)和空调器，该热泵系统(100)包括压缩机组件(10)、室外换热器(20)、室内换热器(30)、加热蓄热装置(50)及切换装置(40)，加热蓄热装置(50)与切换装置(40)串联设置；在第一制热模式下，压缩机组件(10)排出的冷媒经切换装置(40)和加热蓄热装置(50)依次进入室内换热器(30)和室外换热器(20)；在化霜模式下，压缩机组件(10)排出的冷媒经切换装置(40)依次进入室内换热器(30)、室外换热器(20)及加热蓄热装置(50)。

Description

热泵系统及空调器
相关申请的交叉引用
本申请基于申请号为201811253993.8，申请日为2018年10月24日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本申请涉及空调技术领域，特别涉及一种热泵系统及应用所述热泵系统的空调器。
背景技术
热泵系统在制热模式下，制冷剂通过室外换热器从室外侧吸收热量，然后经过压缩机提高压力和温度，将室外侧的热量排到室内达到制热的效果。但在冬天，室外的温度越低，室外换热器内的冷媒因为需要吸收室外空气的热量，需要低于室外空气的温度，这就会导致室外换热器会在制热模式下结霜，结霜后需要通过除霜来保证系统能够安全有效运行。
现有的热泵系统在除霜过程中，需要从室内侧吸热，导致室内温度降低，室内机不能正常制热，并且在室外机重新恢复制热模式时，需要一段时间切换和启动压缩机逐渐加热冷媒系统，从而降低了运行能效。
此外，在外界气温较低时，压缩机排出的冷冻油与液态冷媒互溶性很强，经油分离器分离后，返回压缩机的冷冻油大部分是液态冷媒，压缩机中的冷冻油浓度迟迟上升不到安全浓度。为了保证系统可靠性，现有的热泵系统需要低频运转较长时间，将压缩机中的液态冷媒气化，降低油分离器返回的冷冻油中冷媒的含量，提升压缩机中冷冻油含量至安全浓度后，才能正常运转，此过程持续时间较长，室内机甚至在开机十几分钟后仍然没有热风吹出，启动速度较慢。
发明内容
本申请的主要目的是提供一种热泵系统，旨在使得热泵系统可以在保证室内机正常制热的情况下，实现不停机除霜，提高运行能效和室内的制热舒适性。此外，在低温启动过程时，为压缩机排出的低温气液混合态冷媒提供热量，将压缩机排出的冷冻油中所含的液态冷媒尽快蒸发，迅速降低油分离器返回的冷冻油中冷媒的含量，使得压缩机中的冷冻油浓度迅速提高至安全水平，从而减少压缩机启动至高频运转所需的时间，加快系统启动速度。
为实现上述目的，本申请提出的热泵系统，包括压缩机组件、室外换热器及室内换热器，所述热泵系统还包括：加热蓄热装置和切换装置；所述压缩机组件、切换装置、室外换热器及室内换热器依次连接形成制冷回路，所述加热蓄热装置与所述切换装置串联设置；
所述热泵系统在所述切换装置的切换下具有第一制热模式、第二制热模式及化霜模式，其中，在所述第一制热模式下，所述压缩机组件排出的冷媒经所述切换装置和所述加热蓄热装置依次进入所述室内换热器和室外换热器，并流回至压缩机组件；在所述第二制热模式下，所述压缩机组件排出的冷媒经所述切换装置依次进入所述室内换热器和室外换热器，并流回至压缩机组件；在所述化霜模式下，所述压缩机组件排出的冷媒经所述切换装置依次进入所述室内换热器和室外换热器，从所述室外换热器流出的冷媒经所述加热蓄热装置流回所述压缩机组件。
进一步地，所述切换装置包括串联设置第一四通阀和第二四通阀，所述第一四通阀具有第一至第四阀口，所述第二四通阀具有第五至第八阀口，所述压缩机组件与所述第一阀口连通，所述室外换热器与所述第八阀口连通，所述加热蓄热装置的一端与所述第四阀口连通，另一端与所述第五阀口连通，所述室内换热器与所述第二阀口和第六阀口连通，所述第三阀口和第七阀口均与所述压缩机组件的吸气端连通；
在所述第一制热模式下，所述第一四通阀的第一阀口和第四阀口导通，所述第二四通阀的第五阀口和第六阀口、第七阀口和第八阀口分别导通；
在所述第二制热模式下，所述第一四通阀的第一阀口和第二阀口导通，所述第二四通阀的第七阀口和第八阀口导通；
在所述化霜模式下，所述第一四通阀的第一阀口和第二阀口、第三阀口和第四阀口分别导通，所述第二四通阀的第五阀口和第八阀口导通。
进一步地，所述切换装置还包括第一电磁阀，所述第一电磁阀设于所述第六阀口和所述室内换热器之间。
进一步地，所述热泵系统还包括第一单向阀，所述第一单向阀连接于所述室外换热器和所述加热蓄热装置之间。
进一步地，所述热泵系统还包括节流装置，所述节流装置的一端与所述加热蓄热装置连通，另一端与所述第五阀口和所述第一单向阀连通。
进一步地，所述热泵系统还包括第二单向阀，所述第二单向阀连接于所述第二阀口和所述室内换热器之间。
进一步地，所述热泵系统在所述切换装置的切换下还具有制冷模式，在所述制冷模式下，所述第一四通阀的第一阀口和第四阀口导通，所述第二四通阀的第五阀口和第八阀口、第六阀口和第七阀口分别导通。
进一步地，所述加热蓄热装置包括第二电磁阀和热交换器，所述热交换器串联所述第二电磁阀连通所述切换装置；
所述加热蓄热装置还包括加热组件和/或蓄热组件，所述加热组件和/或蓄热组件设置于所述热交换器的外壁。
进一步地，所述加热组件为外源性加热器；
且/或，所述蓄热组件为蓄热器。
本申请还提出一种空调器，所述空调器包括热泵系统；
热泵系统，包括压缩机组件、室外换热器及室内换热器，所述热泵系统还包括：加热蓄热装置和切换装置；所述压缩机组件、切换装置、室外换热器及室内换热器依次连接形成制冷回路，所述加热蓄热装置与所述切换装置串联设置；
所述热泵系统在所述切换装置的切换下具有第一制热模式、第二制热模式及化霜模式，其中，在所述第一制热模式下，所述压缩机组件排出的冷媒经所述切换装置和所述加热蓄热装置依次进入所述室内换热器和室外换热器，并流回至压缩机组件；在所述第二制热模式下，所述压缩机组件排出的冷媒经所述切换装置依次进入所述室内换热器和室外换热器，并流回至压缩机组件；在所述化霜模式下，所述压缩机组件排出的冷媒经所述切换装置依次进入所述室内换热器和室外换热器，从所述室外换热器流出的冷媒经所述加热蓄热装置流回所述压缩机组件。
本申请技术方案的热泵系统在第一制热模式时，冷媒由压缩机组件排出后经切换装置和加热蓄热装置依次进入室内换热器和室外换热器，并流回至压缩机组件，在此过程中由于冷媒经加热蓄热装置加热，提高了整个热泵系统运行能效，加快了开机启动速度；热泵系统开机启动并正常运行时可在第一制热模式和第二制热模式之间切换，在第二制热模式时，冷媒由压缩机组件排出后经切换装置依次进入室内换热器和室外换热器，并流回至压缩机组件，此过程中以保证热泵系统的正常制热；
进一步地，热泵系统在化霜模式下进行除霜时，冷媒由压缩机组件排出的高温高压冷媒在室内换热器部分冷凝后，流至室外换热器以对室外换热器进行化霜，从室外换热器流出的冷媒经加热蓄热装置吸收热量蒸发流回压缩机组件，从而实现不停制热化霜，在化霜期间同时保持室内温度不下降，提高了热泵系统的运行能效和制热舒适度。本申请提出的热泵系统通过采用切换装置对压缩机组件排出的冷媒进行不同模式的切换，利用加热蓄热装置以使得该热泵系统在制热的同时实现不停制热化霜，提高系统运行能效和制热舒适度。
附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技 术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1为本申请热泵系统在第一制热模式中冷媒流向示意图；
图2为本申请热泵系统在第二制热模式中冷媒流向示意图；
图3为本申请热泵系统在化霜模式中冷媒流向示意图；
图4为本申请热泵系统在制冷模式中冷媒流向示意图。
附图标号说明：
标号 名称 标号 名称
100 热泵系统 D1 第四阀口
10 压缩机组件 42 第二四通阀
11 压缩机 A2 第五阀口
111 排气口 B2 第六阀口
112 回液口 C2 第七阀口
12 分液器 D2 第八阀口
20 室外换热器 43 第一电磁阀
30 室内换热器 50 加热蓄热装置
40 切换装置 51 加热组件
41 第一四通阀 52 热交换器
A1 第一阀口 60 第一单向阀
B1 第二阀口 70 节流装置
C1 第三阀口 80 第二单向阀
本申请目的的实现、功能特点及优点将结合实施例，参照附图做进一步说明。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明，本申请实施例中所有方向性指示(诸如上、下、左、右、前、后……)仅用于解释在某一特定姿态(如附图所示)下各部件之间的相对位置关系、运动情况等，如 果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，在本申请中涉及“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本申请要求的保护范围之内。
本申请提出一种热泵系统100。
参见图1至图4所示，在本申请实施例中，热泵系统100包括压缩机组件10、室外换热器20、室内换热器30、加热蓄热装置50及切换装置40，压缩机组件10、切换装置40、室外换热器20及室内换热器30依次连接形成制冷回路，加热蓄热装置50与切换装置40串联设置。
热泵系统100在切换装置40的切换下具有第一制热模式、第二制热模式及化霜模式，其中，在第一制热模式下，压缩机组件10排出的冷媒经切换装置40和加热蓄热装置50依次进入室内换热器30和室外换热器20，并流回至压缩机组件10；在第二制热模式下，压缩机组件10排出的冷媒经切换装置40依次进入室内换热器30和室外换热器20，并流回至压缩机组件10；在化霜模式下，压缩机组件10排出的冷媒经切换装置40依次进入室内换热器30和室外换热器20，从室外换热器20流出的冷媒经加热蓄热装置50流回压缩机组件10。
具体地，压缩机组件10包括串联设置的压缩机11和分液器12，压缩机组件10具有排汽口111和回液口112，排汽口111设于压缩机11，回液口112设于分液器12，压缩机11的排汽口111与切换装置40连接，用于为排出高温高压的过热蒸气。
在本实施例中，热泵系统100在切换装置40的切换下具有第一制热模式、第二制热模式及化霜模式。可以理解的，热泵系统100在第一制热模式下时，冷媒由压缩机11的排汽口111排出经切换装置40和加热蓄热装置50依次进入室内换热器30和室外换热器20，并由回液口112流回至分液器12，再次流入压缩机11内。该过程中，冷媒经加热蓄热装置50进一步加热，使得在室内换热器30放热后，冷媒的温度仍比较高，在室外换热器20处吸热时，使得室外换热器20不发生结霜现象，从而提高了整个热泵系统100的运行能效，加快了开机启动速度。
热泵系统100在正常开机运行后，经切换装置40切换至第二制热模式，该第二制热模式为正常制热模式，热泵系统100在第二制热模式时，冷媒由压缩机11的排汽口111排出经切换装置40依次进入室内换热器30和室外换热器20，并由回液口112流回至分液器12， 再次流入压缩机11内。该过程中，由压缩机11的排汽口111排出的高温高压的冷媒在室内换热器30放热，以对室内环境进行升温，并在室外换热器20处吸热，实现正常的纯制热模式。可以理解的，热泵系统100在正常开机运行后，热泵系统100也可以在第一制热模式和第二制热模式之间进行切换。
该热泵系统100在化霜模式下进行除霜时，冷媒由压缩机11的排汽口111排出经在室内换热器30部分冷凝后，流至室外换热器20以对室外换热器20进行化霜，从室外换热器20流出的冷媒经加热蓄热装置40吸收热量蒸发由回液口112流回至分液器12，再次流入压缩机11内，从而实现不停制热化霜，在化霜期间同时保持室内温度不下降，提高了热泵系统100的运行能效和制热舒适度。
本申请提出的热泵系统100通过采用切换装置40对压缩机组件10排出的冷媒进行不同模式的切换，利用加热蓄热装置40以使得该热泵系统100在制热的同时实现不停制热化霜，提高系统运行能效和制热舒适度。
进一步地，结合参照图1至图3所示，在本实施例中，切换装置40包括串联设置第一四通阀41和第二四通阀42。第一四通阀41具有第一阀口A1、第二阀口B1、第三阀口C1和第四阀口D1；第二四通阀42具有第五阀口A2、第六阀口B2、第七阀口C2和第八阀口D2。
具体地，压缩机组件10与第一阀口A1连通，室外换热器20与第八阀口D2连通，加热蓄热装置50的一端与第四阀口D1连通，另一端与第五阀口A2连通，室内换热器30与第二阀口B1和第六阀口B2连通，第三阀口C1和第七阀口C2均与压缩机组件10的吸气端连通。可以理解的，本申请的热泵系统100通过切换第一四通阀41和第二四通阀42的阀口，以实现不同模式之间的切换，并利用加热蓄热装置50配合不同模式，从而使热泵系统100实现快速开机启动、正常制热以及不停制热化霜等功能，提高系统运行能效和制热舒适度。
本实施例中，热泵系统100在第一制热模式下，第一四通阀41的第一阀口A1和第四阀口D1导通，第二四通阀42的第五阀口A2和第六阀口B2、第七阀口C2和第八阀口D2分别导通。冷媒由压缩机11的排汽口111排出经第一四通阀41的第一阀口A1和第四阀口D1，由加热蓄热装置50进一步加热，经由第二四通阀42的第五阀口A2和第六阀口B2后，进入室内换热器30放热，此时冷媒的温度仍比较高，在室外换热器20处吸热后，再由第二四通阀42的第八阀口D2和第七阀口C2流出，并由回液口112流回至分液器12，再次流入压缩机11内。较高温度的冷媒在室外换热器20处吸热后，使得室外换热器20不发生结霜现象，从而提高了整个热泵系统100的运行能效，加快了开机启动速度。
热泵系统100在第二制热模式下，第一四通阀41的第一阀口A1和第二阀口B1导通， 第二四通阀42的第七阀口C2和第八阀口D2导通。冷媒由压缩机11的排汽口111排出经第一四通阀41的第一阀口A1和第二阀口B1，进入室内换热器30放热，对室内环境进行升温，并在室外换热器20处吸热，再由第二四通阀42的第八阀口D2和第七阀口C2流出，并由回液口112流回至分液器12，再次流入压缩机11内，实现正常的纯制热模式。
热泵系统100在化霜模式下，第一四通阀41的第一阀口A1和第二阀口B1、第三阀口C1和第四阀口D1分别导通，第二四通阀42的第五阀口A2和第八阀口D2导通。冷媒由压缩机11的排汽口111排出经第一四通阀41的第一阀口A1和第二阀口B1，进入室内换热器30放热，对室内环境进行升温，并在室外换热器20处吸热，再由第二四通阀42的第八阀口D2和第五阀口A2流出，经加热蓄热装置40吸收热量蒸发由回液口112流回至分液器12，再次流入压缩机11内。在此过程中，热泵系统100实现了不停制热化霜，在化霜期间同时保持室内温度不下降，提高了热泵系统100的运行能效和制热舒适度。
进一步地，如图4所示，热泵系统100在切换装置40的切换下还具有制冷模式，也即热泵系统100的正常制冷模式。热泵系统100在制冷模式下，第一四通阀41的第一阀口A1和第四阀口D1导通，第二四通阀42的第五阀口A2和第八阀口D2、第六阀口B2和第七阀口C2分别导通。冷媒由压缩机11的排汽口111排出经第一四通阀41的第一阀口A1和第四阀口D1，并流经加热蓄热装置40后，此时加热蓄热装置40对高温高压的冷媒进行部分吸热或储热，再由第二四通阀42的第五阀口A2和第八阀口D2流入室外换热器20放热，并在室内换热器30吸热，以对室内环境进行降温，再由第二四通阀42的第六阀口B2和第七阀口C2流出，由回液口112流回至分液器12，再次流入压缩机11内。
进一步地，如图1至图4所示，在本实施例中，切换装置40还包括第一电磁阀43，第一电磁阀43设于第六阀口B2和室内换热器30之间。可以理解的，第一电磁阀43的设置，在切换装置40对不同模式进行切换时，有利于第一电磁阀43和第二四通阀42配合，顺利实现不同模式直接的切换。
进一步地，如图1至图4所示，在本实施例中，热泵系统100还包括节流装置70和第一单向阀60，第一单向阀60连接于室外换热器20和加热蓄热装置50之间，节流装置70的一端与加热蓄热装置50连通，另一端与第五阀口A2和第一单向阀60连通。可以理解的，节流装置70为电子膨胀阀或毛细管。
进一步地，如图1至图4所示，在本实施例中，热泵系统100还包括第二单向阀80，第二单向阀80连接于第二阀口B1和室内换热器30之间。
具体地，热泵系统100在第一制热模式下，打开节流装置70和第一电磁阀43，关闭第一单向阀60和第二单向阀80，第一四通阀41的第一阀口A1和第四阀口D1将压缩机11的排汽口111与加热蓄热装置50连通，第二四通阀42的第五阀口A2和第六阀口B2将加 热蓄热装置50和第一电磁阀43、室内换热器30连通。压缩机11的排汽口111排出的高压气态冷媒在加热蓄热装置50中被加热(或冷凝放出一部分热量给加热蓄热装置50)后，经第一电磁阀43送入室内换热器30放热，从室内换热器30流出的液态冷媒在室外换热器20中吸热蒸发成气态冷媒，经第二四通阀42的第八阀口D2和第七阀口C2流出，并由回液口112流回至分液器12，再次流入压缩机11内。
热泵系统100在第二制热模式下，关闭节流装置70、第一电磁阀43及第一单向阀60，打开第二单向阀80，第一四通阀41的第一阀口第二阀口B1将压缩机11的排汽口111与第二单向阀80、室内换热器30连通，压缩机11的排汽口111排出的高压气态冷媒经第一四通阀41、第二单向阀80流向室内换热器30放热，对室内环境进行升温，高压液态冷媒在室外换热器20中吸热蒸发成气态冷媒，经第二四通阀42的的第八阀口D2和第七阀口C2流出，并由回液口112流回至分液器12，再次流入压缩机11内，实现正常的纯制热模式。
热泵系统100在化霜模式下，打开节流装置70、第一单向阀60及第二单向阀80，关闭第一电磁阀43，第一四通阀41的第一阀口第二阀口B1将压缩机11的排汽口111与第二单向阀80、室内换热器30连通，压缩机11的排汽口111排出的高压气态冷媒经第一四通阀41、第二单向阀80流向室内换热器30放热，对室内环境进行升温，冷媒在室外换热器20继续冷凝放出热量，融化室外换热器20上的结霜，产生的液态冷媒经第一单向阀60和节流装置70，流经加热蓄热装置40吸收热量蒸发，并经由第一四通阀41的第四阀口D1和第三阀口C1流入回液口112流回至分液器12，再次流入压缩机11内，从而使热泵系统100实现不停制热化霜，在化霜期间同时保持室内温度不下降，提高了热泵系统100的运行能效和制热舒适度。
可以理解的，在化霜模式下，由室外换热器20流向加热蓄热装置40的过程中产生两条流路。第一条流路为由室外换热器20经第一单向阀60和节流装置70流入加热蓄热装置40中；第二条流路为由室外换热器20经第二四通阀42的第八阀口D2和第五阀口A2、节流装置70流入加热蓄热装置40中。在此过程中，两条流路受压力影响，通常冷媒从第一条流路流向加热蓄热装置40，此时，第二四通阀42暂时失去作用。
热泵系统100在制冷模式下，打开节流装置70和第一单向阀60，关闭第一单向阀60和第二单向阀80，第一四通阀41的第一阀口A1和第四阀口D1将压缩机11的排汽口111与加热蓄热装置50连通，第二四通阀42的第五阀口A2和第八阀口D2将加热蓄热装置50和室外换热器20连通，第二四通阀42的第六阀口B2和第七阀口C2将室内换热器30和分液器12的回液口112连通。压缩机11的排汽口111排出的高压气态冷媒经第一四通阀41、节流装置70、第二四通阀42后，流入室外换热器20冷凝为高压液态冷媒，流入室内换热 器30中节流蒸发为低压气态冷媒，经第二四通阀42的第六阀口B2和第七阀口C2流出，由回液口112流回至分液器12，再次流入压缩机11内，以实现对室内环境进行降温。
进一步地，如图1至图4所示，在一实施中，加热蓄热装置50包括第二电磁阀、热交换器52及加热组件51，加热组件51设置于热交换器52的外壁，热交换器52串联第二电磁阀连通切换装置40。可以理解的，第二电磁阀用于控制热交换器和加热组件51的工作状态。加热组件51为外源性加热器，外源性加热器可以是电加热或燃气加热装置。
在本实施例中，加热组件51优选采用电加热，电加热贴附于热交换器52的外壁，通过第二电磁阀控制电加热，以实现对热交换器52的外壁加热，冷媒在通过热交换器52时，能够通过热交换器52实现热量交换。
在另一实施中，加热蓄热装置50包括第二电磁阀、热交换器52及蓄热组件(未图示)，蓄热组件设置于热交换器52的外壁，热交换器52串联第二电磁阀连通切换装置40。可以理解的，第二电磁阀用于控制热交换器的工作状态，蓄热组件可以是蓄热器，蓄热器可以是利用蓄热材料进行热交换，优选的，蓄热材料可以是相变材料或显热蓄热材料，在此不做限定。蓄热组件优选采用蓄热材料制成的蓄热片，蓄热片设置于热交换器52的外壁，当温度较高的冷媒通过热交换器52进行热量交换时，蓄热片通过热交换器52进行蓄热。蓄热片储蓄的热量用于较低温度的液态冷媒返回压缩机时将液态冷媒汽化，从而降低分液器12返回的冷冻油中冷媒的含量，提升压缩机中冷冻油含量至安全浓度后，实现正常运转，从而减少压缩机启动至高频运转所需的时间，加快系统启动速度。
在第三实施例中，如图1至图4所示，加热蓄热装置50包括第二电磁阀、热交换器52、加热组件51及蓄热组件(未图示)，加热组件51和蓄热组件间隔设置于热交换器52的外壁，热交换器52串联第二电磁阀连通切换装置40。
具体地，第二电磁阀用于控制热交换器和加热组件51的工作状态。加热组件51为外源性加热器，外源性加热器可以是电加热或燃气加热装置；蓄热组件可以是蓄热器，蓄热器可以是利用蓄热材料进行热交换，优选的，蓄热材料可以是相变材料或显热蓄热材料，在此不做限定。在本实施例中，加热组件51优选采用电加热，电加热贴附于热交换器52的外壁，通过第二电磁阀控制电加热，以实现对热交换器52的外壁加热，冷媒在通过热交换器52时，能够通过热交换器52实现热量交换。蓄热组件优选采用蓄热材料制成的蓄热片，蓄热片设置于热交换器52的外壁，当加热组件51对热交换器52的外壁进行加热，冷媒通过热交换器52时进行热量交换的同时，蓄热片也通过热交换器52进行蓄热；或当温度较高的冷媒通过热交换器52进行热量交换时，蓄热片也通过热交换器52进行蓄热。蓄热片储蓄的热量用于较低温度的液态冷媒返回压缩机时将液态冷媒汽化，从而降低分液器12返回的冷冻油中冷媒的含量，提升压缩机中冷冻油含量至安全浓度后，实现正常运转， 从而减少压缩机启动至高频运转所需的时间，加快系统启动速度。
本申请还提出一种空调器，该空调器包括热泵系统100，该热泵系统的具体结构参照上述实施例，由于本热泵系统的控制方法采用了上述所有实施例的全部技术方案，因此至少具有上述实施例的技术方案所带来的所有有益效果，在此不再一一赘述。
本申请的空调器包括热泵系统100，热泵系统100通过采用切换装置40对压缩机组件10排出的冷媒进行不同模式的切换，利用加热蓄热装置50配合切换装置40，使得该热泵系统100在制热的同时实现不停制热化霜，从而提高空调器的运行能效和制热舒适度。
以上所述仅为本申请的优选实施例，并非因此限制本申请的专利范围，凡是在本申请的申请构思下，利用本申请说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本申请的专利保护范围内。

Claims (10)

  1. 一种热泵系统，包括压缩机组件、室外换热器及室内换热器，其特征在于，所述热泵系统还包括：加热蓄热装置和切换装置；所述压缩机组件、切换装置、室外换热器及室内换热器依次连接形成制冷回路，所述加热蓄热装置与所述切换装置串联设置；
    所述热泵系统在所述切换装置的切换下具有第一制热模式、第二制热模式及化霜模式，其中，在所述第一制热模式下，所述压缩机组件排出的冷媒经所述切换装置和所述加热蓄热装置依次进入所述室内换热器和室外换热器，并流回至压缩机组件；在所述第二制热模式下，所述压缩机组件排出的冷媒经所述切换装置依次进入所述室内换热器和室外换热器，并流回至压缩机组件；在所述化霜模式下，所述压缩机组件排出的冷媒经所述切换装置依次进入所述室内换热器和室外换热器，从所述室外换热器流出的冷媒经所述加热蓄热装置流回所述压缩机组件。
  2. 如权利要求1所述的热泵系统，其特征在于，所述切换装置包括串联设置第一四通阀和第二四通阀，所述第一四通阀具有第一至第四阀口，所述第二四通阀具有第五至第八阀口，所述压缩机组件与所述第一阀口连通，所述室外换热器与所述第八阀口连通，所述加热蓄热装置的一端与所述第四阀口连通，另一端与所述第五阀口连通，所述室内换热器与所述第二阀口和第六阀口连通，所述第三阀口和第七阀口均与所述压缩机组件的吸气端连通；
    在所述第一制热模式下，所述第一四通阀的第一阀口和第四阀口导通，所述第二四通阀的第五阀口和第六阀口、第七阀口和第八阀口分别导通；
    在所述第二制热模式下，所述第一四通阀的第一阀口和第二阀口导通，所述第二四通阀的第七阀口和第八阀口导通；
    在所述化霜模式下，所述第一四通阀的第一阀口和第二阀口、第三阀口和第四阀口分别导通，所述第二四通阀的第五阀口和第八阀口导通。
  3. 如权利要求2所述的热泵系统，其特征在于，所述切换装置还包括第一电磁阀，所述第一电磁阀设于所述第六阀口和所述室内换热器之间。
  4. 如权利要求3所述的热泵系统，其特征在于，所述热泵系统还包括第一单向阀，所述第一单向阀连接于所述室外换热器和所述加热蓄热装置之间。
  5. 如权利要求4所述的热泵系统，其特征在于，所述热泵系统还包括节流装置，所述节流装置的一端与所述加热蓄热装置连通，另一端与所述第五阀口和所述第一单向阀连通。
  6. 如权利要求2至5中任一项所述的热泵系统，其特征在于，所述热泵系统还包括第二单向阀，所述第二单向阀连接于所述第二阀口和所述室内换热器之间。
  7. 如权利要求6所述的热泵系统，其特征在于，所述热泵系统在所述切换装置的切换下还具有制冷模式，在所述制冷模式下，所述第一四通阀的第一阀口和第四阀口导通，所述第二四通阀的第五阀口和第八阀口、第六阀口和第七阀口分别导通。
  8. 如权利要求1所述的热泵系统，其特征在于，所述加热蓄热装置包括第二电磁阀和热交换器，所述热交换器串联所述第二电磁阀连通所述切换装置；
    所述加热蓄热装置还包括加热组件和/或蓄热组件，所述加热组件和/或蓄热组件设置于所述热交换器的外壁。
  9. 如权利要求8所述的热泵系统，其特征在于，所述加热组件为外源性加热器；
    且/或，所述蓄热组件为蓄热器。
  10. 一种空调器，其特征在于，所述空调器包括如权利要求1至9中任一项所述的热泵系统。
PCT/CN2019/089266 2018-10-24 2019-05-30 热泵系统及空调器 WO2020082735A1 (zh)

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Publication number Priority date Publication date Assignee Title
CN109405335B (zh) * 2018-10-24 2020-05-22 广东美的暖通设备有限公司 热泵系统及空调器
CN111780465A (zh) * 2020-06-22 2020-10-16 上海爱斯达克汽车空调系统有限公司 无需停机的电动汽车热泵除霜系统及其运行方法
CN115076966A (zh) * 2021-03-15 2022-09-20 广东美的暖通设备有限公司 空调器的控制方法及装置
CN113587469B (zh) * 2021-08-02 2022-11-15 珠海格力节能环保制冷技术研究中心有限公司 一种温控系统的控制装置、方法和温控系统
CN114110846B (zh) * 2021-11-23 2023-05-02 珠海格力电器股份有限公司 一种蓄能热泵系统及其控制方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009287903A (ja) * 2008-06-02 2009-12-10 Kansai Electric Power Co Inc:The 蓄熱式ヒートポンプ装置
CN103791569A (zh) * 2012-10-30 2014-05-14 珠海格力电器股份有限公司 热泵式空调系统
CN203964489U (zh) * 2014-07-01 2014-11-26 珠海格力电器股份有限公司 空调热泵系统
CN108224840A (zh) * 2018-01-25 2018-06-29 珠海格力电器股份有限公司 一种热泵空调系统和控制方法
CN109405335A (zh) * 2018-10-24 2019-03-01 广东美的暖通设备有限公司 热泵系统及空调器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63116073A (ja) * 1986-10-31 1988-05-20 株式会社東芝 蓄熱式ヒ−トポンプ
KR101436637B1 (ko) * 2008-01-21 2014-09-01 엘지전자 주식회사 냉난방 시스템 및 그 제어방법
CN105865073B (zh) * 2016-04-18 2018-06-01 广东美的制冷设备有限公司 空调系统及其控制方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009287903A (ja) * 2008-06-02 2009-12-10 Kansai Electric Power Co Inc:The 蓄熱式ヒートポンプ装置
CN103791569A (zh) * 2012-10-30 2014-05-14 珠海格力电器股份有限公司 热泵式空调系统
CN203964489U (zh) * 2014-07-01 2014-11-26 珠海格力电器股份有限公司 空调热泵系统
CN108224840A (zh) * 2018-01-25 2018-06-29 珠海格力电器股份有限公司 一种热泵空调系统和控制方法
CN109405335A (zh) * 2018-10-24 2019-03-01 广东美的暖通设备有限公司 热泵系统及空调器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3680578A4 *

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