CN114484618B - Air conditioner and control method thereof - Google Patents

Air conditioner and control method thereof Download PDF

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Publication number
CN114484618B
CN114484618B CN202210089907.4A CN202210089907A CN114484618B CN 114484618 B CN114484618 B CN 114484618B CN 202210089907 A CN202210089907 A CN 202210089907A CN 114484618 B CN114484618 B CN 114484618B
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CN
China
Prior art keywords
compressor
air conditioner
pipeline
expansion valve
indoor unit
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Application number
CN202210089907.4A
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Chinese (zh)
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CN114484618A (en
Inventor
薛秀夫
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Aux Air Conditioning Co Ltd
Ningbo Aux Electric Co Ltd
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Aux Air Conditioning Co Ltd
Ningbo Aux Electric Co Ltd
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Priority to CN202210089907.4A priority Critical patent/CN114484618B/en
Publication of CN114484618A publication Critical patent/CN114484618A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/08—Compressors specially adapted for separate outdoor units
    • F24F1/10—Arrangement or mounting thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/48—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring prior to normal operation, e.g. pre-heating or pre-cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Thermal Sciences (AREA)
  • Signal Processing (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

The embodiment of the invention provides an air conditioner and a control method thereof, belonging to the technical field of air conditioners. The air conditioner includes a first compressor, a second compressor, and a first pipe. The exhaust port of the second compressor is in communication with the intake port of the first compressor, and the exhaust port of the second compressor is in communication with the intake port of the second compressor through a first conduit. The exhaust port of the first compressor and the air inlet of the second compressor are used for exchanging heat with the indoor unit. The air conditioner is provided with a first refrigerant circulation flow path and a second refrigerant circulation flow path which run simultaneously in an operating state, wherein an air inlet of the second compressor, an air outlet of the second compressor and a first pipeline in the first refrigerant circulation flow path are communicated in a closed loop manner, and an air inlet of the second compressor, an air outlet of the second compressor, an air inlet of the first compressor, an air outlet of the first compressor and a heat exchanger of the indoor unit in the second refrigerant circulation flow path are communicated in a closed loop manner. The time for starting the air conditioner at an extremely low temperature is shortened.

Description

Air conditioner and control method thereof
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air conditioner and an air conditioner control method.
Background
In recent years, heat pump air conditioning apparatuses have been increasingly used, and the demand for performing heating operation in an extremely low-temperature environment having a lower ambient temperature has also increased.
However, when the conventional air conditioner is started at an extremely low temperature, the temperature of the refrigerant in the refrigerant circuit is low, so that the air conditioner needs a long starting time when the air conditioner is started at the heating.
Disclosure of Invention
The invention solves the problem that the existing air conditioner needs longer starting time when heating and starting because the temperature of the refrigerant in the refrigerant loop is lower when the air conditioner is started at very low temperature.
In order to solve the above problems, embodiments of the present invention provide an air conditioner and a control method of the air conditioner, which can reduce the time for heating start of the air conditioner at an extremely low temperature.
In a first aspect, the present invention provides an air conditioner including a first compressor, a second compressor, and a first pipe; the exhaust port of the second compressor is communicated with the air inlet of the first compressor, and the exhaust port of the second compressor is communicated with the air inlet of the second compressor through the first pipeline; the exhaust port of the first compressor and the air inlet of the second compressor are used for being connected with an indoor unit heat exchanger; the air conditioner is provided with a first refrigerant circulation flow path and a second refrigerant circulation flow path which are operated simultaneously in an operation state, wherein an air inlet of the second compressor, an air outlet of the second compressor and the first pipeline in the first refrigerant circulation flow path are communicated in a closed loop manner, and an air inlet of the second compressor, an air outlet of the second compressor, an air inlet of the first compressor, an air outlet of the first compressor and a heat exchanger of the indoor unit in the second refrigerant circulation flow path are communicated in a closed loop manner.
According to the application, the first compressor and the second compressor are connected in series, and the exhaust port and the air inlet of the second compressor are communicated through the first pipeline, so that the air conditioner is provided with a first refrigerant circulation flow path and a second refrigerant circulation flow path which run simultaneously when the air conditioner is started for heating, the air inlet of the second compressor in the first refrigerant circulation flow path, the exhaust port of the second compressor and the first pipeline are communicated in a closed loop, and the air inlet of the second compressor, the exhaust port of the second compressor, the air inlet of the first compressor, the exhaust port of the first compressor and the heat exchanger of the indoor unit are communicated in a closed loop. Therefore, the second refrigerant circulation flow path can maintain the normal heating cycle of the indoor unit. Meanwhile, the temperature of the refrigerant at the air inlet of the second compressor can be increased by utilizing the first refrigerant circulating flow path to lead the refrigerant compressed by the second compressor into the second compressor through the first pipeline, so that the temperature of the refrigerant in the refrigerant loop is increased, and the starting time of the air conditioner during heating and starting can be shortened.
In an optional embodiment, the air conditioner further comprises a first valve body, wherein the first valve body is arranged on the first pipeline and is used for controlling on-off of the first pipeline; the air conditioner is provided with a first operation state in which the first valve body is opened, and the first refrigerant circulation flow path and the second refrigerant circulation flow path simultaneously operate in the first operation state; the air conditioner is also provided with a second running state in which the first valve body is closed, and in the second running state, the air inlet of the second compressor, the air outlet of the second compressor, the air inlet of the first compressor, the air outlet of the first compressor and the heat exchanger of the indoor unit are communicated in a closed loop. Through setting up first valve body, when entering steady heat state after the air conditioner heats the start-up, first valve body can block the gas vent of second compressor and the air inlet intercommunication of second compressor to make the air conditioner more energy-conserving when heating the operation.
In an alternative embodiment, the air conditioner further comprises a second valve body, a second pipe, a third pipe, and a fourth pipe; the air inlet of the first compressor is communicated with the air inlet of the second compressor through the second pipeline; the exhaust port of the second compressor is communicated with the exhaust port of the first compressor through the third pipeline; the exhaust port of the second compressor is communicated with the air inlet of the first compressor through the fourth pipeline; the second valve body is arranged on the fourth pipeline and is used for controlling the on-off of the fourth pipeline; the air conditioner further has a third operation state in which the first valve body is opened and the second valve body is opened or closed, and in the third operation state, the first compressor and the second compressor are connected in parallel to the indoor unit heat exchanger.
In an alternative embodiment, one end of the second pipe is connected to the air inlet of the first compressor, the other end of the second pipe is connected to one end of the first pipe, the other end of the first pipe is connected to the air inlet of the second compressor, one end of the fourth pipe is connected to the air outlet of the second compressor, and the other end of the fourth pipe is connected to the second pipe; the first pipeline and the third pipeline are used for being communicated with the indoor unit heat exchanger; the air conditioner is in an open state in the first running state, the air inlet of the second compressor, the air outlet of the second compressor, the fourth pipeline and the first pipeline are communicated in a closed loop manner to form a first refrigerant circulation flow path, and the air inlet of the second compressor, the air outlet of the second compressor, the fourth pipeline, the second pipeline, the first compressor air inlet, the first compressor air outlet, the third pipeline, the indoor unit heat exchanger and the first pipeline are communicated in a closed loop manner to form a second refrigerant circulation flow path; the air conditioner is in a second running state, the first valve body is in a closed state, the second valve body is in an open state, and the air inlet of the second compressor, the air outlet of the second compressor, the fourth pipeline, the second pipeline, the first compressor air inlet, the first compressor air outlet, the third pipeline, the indoor unit heat exchanger and the first pipeline are communicated in a closed loop manner to form a refrigerant circulation flow path; in a third running state, the first valve body is in an open state, the second valve body is in a closed state, and the first compressor and the second compressor are connected in parallel.
According to the application, the first valve body and the second valve body are arranged, so that the air conditioner has three operation states during heating operation, and the air conditioner can be selected according to different use environments and use requirements when in use, so that the heating effect of the air conditioner is better, and the air conditioner is more convenient to use and saves energy.
In an alternative embodiment, the air conditioner further includes a reverse pressure flow valve, where the reverse pressure flow valve is disposed in the first pipe, and is configured to limit a flow rate of the refrigerant in the first operation state, so that a part of the refrigerant discharged from the second compressor discharge port flows to the first compressor discharge port, and another part flows to the second compressor intake port, and when the reverse pressure flow valve is further used in the third operation state, the first pipe is turned on, and a part of the refrigerant flows to the first compressor intake port.
By arranging the reverse pressure flow valve, the refrigerant can be limited when the air conditioner operates in a first operation state, one part of the refrigerant flowing out of the second compression exhaust port flows to the air inlet of the first compressor, and the other part flows to the air inlet of the second compressor, so that the normal operation of the first refrigerant circulation flow path and the second refrigerant circulation flow path is ensured. In the third operation state, the refrigerant can flow to the air inlet of the first compressor at a large flow rate.
In an alternative embodiment, the air conditioner further includes a check valve mounted to the third pipe, the check valve for blocking the third pipe in the first and second operating states, and for making the third pipe conductive in the third operating state. The check valve may be arranged to block the third conduit in the first operating condition and the second operating condition, and to allow the third conduit to communicate at a high flow rate in the third operating condition.
In an alternative embodiment, the air conditioner further includes a four-way valve, a fifth pipe, a sixth pipe, an outdoor unit heat exchanger, an outdoor unit expansion valve, and an indoor unit heat exchanger; one end of the fifth pipeline is connected with the third pipeline, so that the refrigerant flowing out of the exhaust port of the first compressor and/or the refrigerant flowing out of the exhaust port of the second compressor can flow into the fifth pipeline, the other end of the fifth pipeline is communicated with the first port of the four-way valve, one end of the sixth pipeline is connected with the first pipeline, the other end of the sixth pipeline is communicated with the third port of the four-way valve, one end of the outdoor unit heat exchanger is communicated with the second port of the four-way valve, the other end of the outdoor unit heat exchanger is communicated with the outdoor unit expansion valve, and one end of the indoor unit heat exchanger is communicated with the fourth port of the four-way valve. The four-way valve is arranged to regulate the flow direction of the refrigerant according to the refrigerating and heating requirements of the air conditioner.
In an optional embodiment, the air conditioner further includes an auxiliary heat exchange assembly, a third valve body and a seventh pipe, the auxiliary heat exchange assembly is connected between the outdoor unit expansion valve and the indoor unit heat exchanger, the auxiliary heat exchange assembly is communicated with the fourth pipe, one end of the seventh pipe is connected with the fourth pipe, the other end of the seventh pipe is connected with the first pipe, the third valve body is arranged in the seventh pipe, and the third valve body is used for controlling on-off of the seventh pipe; in the third operation state, the first valve body is in an open state, the second valve body is in a closed state, the third valve body is in an open state, and the auxiliary heat exchange assembly can convey the heat exchanged refrigerant to the air inlet of the first compressor and the air inlet of the second compressor. The third valve body and the auxiliary heat exchange component are arranged, so that energy can be recovered and reused, and the energy consumption of the air conditioner is reduced.
In a second aspect, the present invention provides a control method for an air conditioner, which is applied to the air conditioner in the foregoing embodiment, and the control method includes:
acquiring outdoor environment temperature;
Judging whether the outdoor environment temperature is lower than a preset outdoor environment temperature or not under the condition of receiving a heating instruction;
if the outdoor environment temperature is lower than the preset outdoor environment temperature, configuring starting operation parameters of the air conditioner, controlling the first valve body and the second valve body to be opened, controlling the first interface and the fourth interface of the four-way valve to be communicated, and controlling the air conditioner to operate according to the first operation state.
The control method of the air conditioner judges whether the outdoor environment temperature is lower than the preset outdoor environment temperature or not under the condition that a heating instruction is received, and when the outdoor environment temperature is lower than the preset outdoor environment temperature, the starting operation parameters of the air conditioner are configured, the first valve body and the second valve body are controlled to be opened, the first interface and the fourth interface of the four-way valve are controlled to be communicated, and the air conditioner is controlled to operate according to the first operation state, so that the air conditioner is provided with a first refrigerant circulation flow path and a second refrigerant circulation flow path which operate simultaneously when the air conditioner is started for heating, an air inlet of the second compressor in the first refrigerant circulation flow path, an air outlet of the second compressor and a first pipeline are communicated in a closed loop, and an air inlet of the second compressor in the second refrigerant circulation flow path, an air outlet of the second compressor, an air inlet of the first compressor, an air outlet of the first compressor and a heat exchanger of the indoor unit are communicated in a closed loop. Therefore, the second refrigerant circulation flow path can maintain the normal heating cycle of the indoor unit. Meanwhile, the temperature of the refrigerant at the air inlet of the second compressor can be increased by utilizing the first refrigerant circulating flow path to lead the refrigerant compressed by the second compressor into the second compressor through the first pipeline, so that the temperature of the refrigerant in the refrigerant loop is increased, and the starting time of the air conditioner during heating and starting can be shortened.
In an alternative embodiment, the step of configuring the start-up operation parameter of the air conditioner includes:
controlling the starting frequency of the first compressor to be one half of the rated starting frequency of the first compressor;
controlling the starting frequency of the second compressor to be twice the starting frequency of the first compressor;
and controlling the opening degree of the outdoor unit expansion valve to be the lowest opening degree.
According to the application, the starting frequency of the first compressor is one half of the rated starting frequency of the first compressor, the starting frequency of the second compressor is twice of the starting frequency of the first compressor, the opening degree of the outdoor unit expansion valve is the lowest opening degree, the circulation volume of the first compressor and the second compressor can be adjusted, and the medium pressure can be adjusted to the pressure with the highest operation efficiency.
In an alternative embodiment, after the step of controlling the air conditioner to operate in the first operation state, the control method further includes:
acquiring the superheat degree of the exhaust port of the second compressor and the superheat degree of the air inlet of the first compressor;
and if the superheat degree of the exhaust port of the first compressor is larger than the preset exhaust heat degree and the superheat degree of the air inlet of the second compressor is larger than the preset suction superheat degree, controlling the air conditioner to perform heating operation in the second operation state or the third operation state.
The application can conveniently judge whether the air conditioner is started to be finished or not through the superheat degree of the exhaust port of the first compressor and the superheat degree of the air inlet of the second compressor, and can control the air conditioner to operate in the second operation state or the third operation state after the air conditioner is started to be finished, so that the heating operation effect of the air conditioner is good, and meanwhile, the operation of the air conditioner is more energy-saving.
In an alternative embodiment, the step of controlling the air conditioner to perform the heating operation in the second operation state or the third operation state includes:
obtaining low pressure values of the first compressor and the second compressor, and/or obtaining compression ratios of the first compressor and the second compressor;
and if the low pressure value of the first compressor and the second compressor is smaller than the preset low pressure value or the compression ratio of the first compressor and the second compressor is larger than the preset compression ratio, controlling the first valve body to be closed and the second valve body to be opened, configuring the operation parameters of the second operation state of the air conditioner, and controlling the air conditioner to operate in the second operation state.
According to the low-pressure value of the first compressor and the second compressor or the compression ratio of the first compressor and the second compressor, the air conditioner can be conveniently controlled to operate in the second operation state or the third operation state, the air conditioner and the environment are more targeted, and therefore the air conditioner is more energy-saving to use.
In an alternative embodiment, the step of controlling the air conditioner to perform the heating operation in the second operation state or the third operation state further includes:
and if the low pressure value of the first compressor and the second compressor is larger than a preset low pressure value or the compression ratio of the first compressor and the second compressor is smaller than a preset compression ratio, controlling the first valve body to be opened and the second valve body to be closed, configuring the operation parameters of the air conditioner in the third operation state, and controlling the air conditioner to operate in the third operation state.
According to the low-pressure value of the first compressor and the second compressor or the compression ratio of the first compressor and the second compressor, the air conditioner can be conveniently controlled to operate in the second operation state or the third operation state, the air conditioner and the environment are more targeted, and therefore the air conditioner is more energy-saving to use.
In an alternative embodiment, the air conditioner further comprises an indoor unit expansion valve, wherein the indoor unit expansion valve is connected in series between the indoor unit heat exchanger and the outdoor expansion valve;
the step of configuring the operating parameters of the second operating state of the air conditioner includes:
Acquiring the air inlet pressure of the second compressor at the current moment, the air outlet pressure of the first compressor at the current moment, the superheat degree of the outlet of the heat exchanger of the outdoor unit at the current moment, the opening degree of the expansion valve of the outdoor unit at the current moment, the current opening degree of the expansion valve of the indoor unit and the supercooling degree of the outlet of the heat exchanger of the indoor unit;
the medium pressure is calculated according to the following formula:
P m ＝(P h *P s )^(1/2)；
P m represents the medium pressure, P h Represents the first compressor discharge pressure, P s Representing a second compressor inlet pressure;
determining a first refrigerant density corresponding to the medium pressure and a second refrigerant density corresponding to the second compressor air inlet pressure according to a refrigerant physical property table;
and calculating the operation frequency of the second compressor at the next moment according to the following formula:
Hz s(t+1) ＝Hz s(t+1) *(ρ m /ρ s )/(1+α)；
Hzs (t+1) representing the operating frequency of the second compressor at the next moment ρ h Represents the first refrigerant density ρ s The density of the second refrigerant is represented, alpha represents the cycle ratio of the spray enthalpy, and the value of alpha is 0.15-0.30;
controlling the next moment of the second compressor to be Hz s(t+1) Is a frequency operation of (2);
calculating a frequency adjustment value of the first compressor according to the following formula:
△Hz h ＝f x (P g -P h )；
△Hz h representing the frequency adjustment value, P, of the first compressor g Representing the target pressure, P h Represents the discharge port pressure of the first compressor;
calculating the operating frequency of the first compressor at the next moment according to the following formula:
△Hz＝f x (P g -P h )；
DeltaHz represents the frequency adjustment value, P g Representing the target pressure, P h Representing the discharge pressure of the first compressor or the discharge pressure of the second compressor;
calculating the operating frequency of the first compressor at the next moment according to the following formula:
Hz h(t+1) ＝Hz h(t) +△Hz；
Hz h(t+1) indicating the operating frequency, hz, of the first compressor at the next moment h(t) Representative bookThe operating frequency of the first compressor at the moment;
controlling the next moment of the first compressor to be Hz h(t+1) Is a frequency operation of (2);
calculating an adjustment value of the opening degree of the expansion valve of the outdoor unit according to the following formula:
△P ls ＝g x (S HG –S H )；
△P ls represents the opening adjustment value of the expansion valve of the outdoor unit, S HG Indicating the target superheat degree S H Indicating the superheat degree of the outlet of the heat exchanger of the outdoor unit;
calculating the opening degree of the expansion valve of the outdoor unit at the next moment according to the following formula;
P ls(t+1) ＝P ls(t) +△P ls ；
P ls(t+1) indicating the opening degree of the expansion valve of the outdoor unit at the next moment, P ls(t) Representing the opening degree of the expansion valve of the outdoor unit at the current moment;
controlling the next moment of the expansion valve of the outdoor unit to be P ls(t+1) Opening degree operation;
calculating an adjustment value of the opening of the expansion valve of the indoor unit according to the following formula:
△P lsc ＝k x (S cG –S c )；
△P lsc s represents the opening adjustment value of the expansion valve of the indoor unit cG Indicating the target supercooling degree S H Indicating the degree of supercooling of the outlet of the heat exchanger of the outdoor unit;
calculating the opening of the expansion valve of the indoor unit at the next moment according to the following formula;
P lsc(t+1) ＝P lsc(t) +△P lsc ；
P lsc(t+1) indicating the opening degree of an expansion valve of the indoor unit at the next moment, P lsc(t) Representing the opening degree of the expansion valve of the indoor unit at the current moment;
controlling the next moment of the expansion valve of the indoor unit to be P ls(t+1) And (5) opening operation.
According to the application, the operation parameters of the air conditioner are adjusted in the second operation state, so that the operation state and the operation parameters of the air conditioner can be more matched, and the heating operation effect of the air conditioner is better.
In an alternative embodiment, the air conditioner further comprises an indoor unit expansion valve, wherein the indoor unit expansion valve is connected in series between the indoor unit heat exchanger and the outdoor expansion valve;
the step of configuring the operating parameters of the third operating state of the air conditioner includes:
acquiring the exhaust port pressures of the first compressor and the second compressor, the operating frequencies of the first compressor and the second compressor and the superheat degree of the outlet of the heat exchanger of the outdoor unit at the current moment, acquiring the opening degree of the expansion valve of the outdoor unit at the current moment, and acquiring the current opening degree of the expansion valve of the indoor unit and the supercooling degree of the outlet of the heat exchanger of the indoor unit;
Calculating the frequency adjustment values of the first compressor and the second compressor according to the following formula:
△Hz＝f x (P g -P h )；
DeltaHz represents the frequency adjustment value of the first compressor and the second compressor, P g Representing the target pressure, P h Representing the discharge pressure of the first compressor or the discharge pressure of the second compressor;
calculating the operating frequencies of the first compressor and the second compressor at the next moment according to the following formula:
Hz (t+1) ＝Hz (t) +△Hz；
Hz (t+1) representing the operating frequency, hz, of the first and second compressors at the next time (t) Representing the operating frequencies of the first compressor and the second compressor at the current moment;
controlling the first compressor and the second compressor at Hz at the next moment (t+1) Frequency operation;
calculating an adjustment value of the opening degree of the expansion valve of the outdoor unit according to the following formula:
△P ls ＝g x (S HG –S H )；
△P ls represents the opening adjustment value of the expansion valve of the outdoor unit, S HG Indicating the target superheat degree S H Indicating the superheat degree of the outlet of the heat exchanger of the outdoor unit;
calculating the opening degree of the expansion valve of the outdoor unit at the next moment according to the following formula;
P ls(t+1) ＝P ls(t) +△Pls；
P ls(t+1) indicating the opening degree of the expansion valve of the outdoor unit at the next moment, P ls(t) Representing the opening degree of the expansion valve of the outdoor unit at the current moment;
controlling the next moment of the expansion valve of the outdoor unit to be P ls(t+1) Opening degree operation;
calculating an adjustment value of the opening of the expansion valve of the indoor unit according to the following formula:
△P lsc ＝k x (S cG –S c )；
△P lsc S represents the opening adjustment value of the expansion valve of the indoor unit cG Indicating the target supercooling degree S H Indicating the degree of supercooling of the outlet of the heat exchanger of the outdoor unit;
calculating the opening of the expansion valve of the indoor unit at the next moment according to the following formula;
P lsc(t+1) ＝P lsc(t) +△P lsc ；
P lsc(t+1) indicating the opening degree of an expansion valve of the indoor unit at the next moment, P lsc(t) Representing the opening degree of the expansion valve of the indoor unit at the current moment;
controlling the next moment of the expansion valve of the indoor unit to be P ls(t+1) And (5) opening operation.
According to the application, in the third operation state, the operation parameters of the air conditioner are adjusted, so that the operation state and the operation parameters of the air conditioner can be more matched, and the heating operation effect of the air conditioner is better.
In an alternative embodiment, when the air conditioner receives a cooling command, the control method includes:
the first interface and the second interface of the four-way valve are controlled to be communicated;
opening the first valve body and closing the second valve body;
configuring refrigeration operation parameters;
and controlling the air conditioner to perform refrigeration operation.
When receiving a refrigeration instruction, the air conditioner disclosed by the application controls the first valve body to be opened and controls the second valve body to be closed, so that the first compressor and the second compressor are connected in series, and the refrigeration effect of the air conditioner is better.
In an alternative embodiment, the step of configuring the refrigeration operation parameter includes:
acquiring the air inlet pressures of the first compressor and the second compressor at the current moment and the running frequencies of the first compressor and the second compressor at the current moment;
calculating the frequency adjustment values of the first compressor and the second compressor according to the following formula:
△Hz＝f x (P g -P s )；
DeltaHz represents the frequency adjustment value of the first compressor and the second compressor, P g Representing the target pressure, P s Representing the inlet pressure of the first compressor or the inlet pressure of the second compressor;
calculating the operating frequencies of the first compressor and the second compressor at the next moment according to the following formula:
Hz (t+1) ＝Hz (t) +△Hz；
Hz (t+1) representing the operating frequency, hz, of the first and second compressors at the next time (t) Representing the operating frequencies of the first compressor and the second compressor at the current moment;
controlling the first compressor and the second compressor at Hz at the next moment (t+1) Frequency operation.
According to the application, the parameters of the air conditioner during refrigeration operation are configured, so that the operation parameters and the operation conditions of the air conditioner during refrigeration operation are more matched, and the refrigeration effect of the air conditioner is better.
Drawings
Fig. 1 is a schematic diagram of an overall structure of an air conditioner according to an embodiment of the present invention;
fig. 2 is a schematic diagram of a refrigerant flow direction of an air conditioner operating in a first operation state according to an embodiment of the present invention;
FIG. 3 is a schematic diagram illustrating a refrigerant flow direction of an air conditioner operating in a second operating state according to an embodiment of the present invention;
fig. 4 is a schematic flow diagram of a refrigerant in a third operation state of the air conditioner according to the embodiment of the present invention;
fig. 5 is a schematic diagram illustrating a refrigerant flow direction of an air conditioner during a cooling operation according to an embodiment of the present invention;
FIG. 6 is a schematic cross-sectional view of a reverse pressure flow valve of an air conditioner according to an embodiment of the present invention;
fig. 7 is a schematic flow chart of a control method of an air conditioner according to an embodiment of the present invention;
fig. 8 is a schematic flow chart of switching from a first operation state to a second operation state or a third operation state in the air conditioner control method according to the embodiment of the present invention;
fig. 9 is a flow chart of a second running state parameter configuration of the air conditioner control method according to the embodiment of the invention;
fig. 10 is a flow chart illustrating a third operational parameter configuration of the air conditioner control method according to the embodiment of the present invention;
FIG. 11 is a schematic flow chart of a control method of an air conditioner according to an embodiment of the present invention;
Fig. 12 is a flow chart illustrating parameter configuration during cooling operation of the air conditioner control method according to the embodiment of the invention.
Reference numerals illustrate:
1-a first compressor; 2-a second compressor; 3-a first pipe; 4-a first valve body; 5-a second valve body; 6-a second pipe; 7-a third pipe; 8-a fourth pipe; 9-a back pressure flow valve; 91-valve seat; 92-valve core; 93-a first flow channel; 94-a second flow channel; 10-check valve; 11-a four-way valve; 12-a fifth pipe; 13-sixth conduit; 14-an outdoor unit heat exchanger; 15-an outdoor unit expansion valve; 16-an indoor unit heat exchanger; 17-an auxiliary heat exchange assembly; 171-an auxiliary heat exchanger; 172-an auxiliary heat exchange expansion valve; 18-a third valve body; 19-seventh conduit; 20-an indoor unit expansion valve; 100-air conditioner.
Detailed Description
When the existing air conditioner is started at extremely low temperature, the temperature of the refrigerant in the refrigerant loop is low, so that the air conditioner needs longer starting time when the air conditioner is started at the temperature of the refrigerant loop. In order that the above objects, features and advantages of the invention will be readily understood, a more particular description of the invention will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings.
Referring to fig. 1 and 2, the present embodiment provides an air conditioner 100, wherein the air conditioner 100 includes a first compressor 1, a second compressor 2 and a first pipe 3; the exhaust port of the second compressor 2 is communicated with the air inlet of the first compressor 1, and the exhaust port of the second compressor 2 is communicated with the air inlet of the second compressor 2 through a first pipeline 3; the exhaust port of the first compressor 1 and the intake port of the second compressor 2 are used for the indoor unit heat exchanger 16; in the operation state of the air conditioner 100, the air conditioner 100 has a first refrigerant circulation path and a second refrigerant circulation path that are simultaneously operated, wherein an air inlet of the second compressor 2, an air outlet of the second compressor 2 and the first pipe 3 in the first refrigerant circulation path are closed-loop communicated, and an air inlet of the second compressor 2, an air outlet of the second compressor 2, an air inlet of the first compressor 1, an air outlet of the first compressor 1 and the indoor unit heat exchanger 16 in the second refrigerant circulation path are closed-loop communicated.
The application connects the first compressor 1 and the second compressor 2 in series, and connects the exhaust port and the air inlet of the second compressor 2 through the first pipeline 3, thereby having a first refrigerant circulation flow path and a second refrigerant circulation flow path which run simultaneously when the air device is heated and started, wherein the air inlet of the second compressor 2 in the first refrigerant circulation flow path, the exhaust port of the second compressor 2 and the first pipeline 3 are communicated in a closed loop, and the air inlet of the second compressor 2, the exhaust port of the second compressor 2, the air inlet of the first compressor 1, the exhaust port of the first compressor 1 and the indoor unit heat exchanger 16 are communicated in a closed loop. Therefore, the second refrigerant circulation flow path can maintain the normal heating cycle of the indoor unit. Meanwhile, the temperature of the refrigerant at the air inlet of the second compressor 2 can be increased by utilizing the first refrigerant circulation flow path to lead the refrigerant compressed by the second compressor 2 into the second compressor 2 through the first pipeline 3, so that the temperature of the refrigerant in the refrigerant loop is increased, and the starting time of the air conditioner 100 during heating and starting can be shortened.
In this embodiment, the air conditioner 100 further includes a first valve body 4, where the first valve body 4 is disposed on the first pipe 3, and the first valve body 4 is used to control on-off of the first pipe 3; the air conditioner 100 has a first operation state in which the first valve body 4 is opened, and in the first operation state, the first refrigerant circulation flow path and the second refrigerant circulation flow path are operated simultaneously; the air conditioner 100 further has a second operation state in which the first valve body 4 is closed, and in the second operation state, the air inlet of the second compressor 2, the air outlet of the second compressor 2, the air inlet of the first compressor 1, the air outlet of the first compressor 1, and the indoor unit heat exchanger are in closed-loop communication. Through setting up first valve body 4, when entering steady warm state after air conditioner 100 heats the start-up, first valve body 4 can block the gas vent of second compressor 2 and the air inlet intercommunication of second compressor 2 to make air conditioner 100 more energy-conserving when heating the operation.
In the present embodiment, the first valve body 4 is a solenoid valve, but in other embodiments of the present application, the first valve body 4 may be another type of electrically controlled valve.
Referring to fig. 1, 2, 3 and 4, in the present embodiment, the air conditioner 100 further includes a second valve body 5, a second pipe 6, a third pipe 7 and a fourth pipe 8; the air inlet of the first compressor 1 is communicated with the air inlet of the second compressor 2 through a second pipeline 6; the exhaust port of the second compressor 2 is communicated with the exhaust port of the first compressor 1 through a third pipeline 7; the exhaust port of the second compressor 2 is communicated with the air inlet of the first compressor 1 through a fourth pipeline 8; the second valve body 5 is arranged on the fourth pipeline 8, and the second valve body 5 is used for controlling the on-off of the fourth pipeline 8; the air conditioner 100 further has a third operation state in which the first valve body 4 is closed and the second valve body 5 is opened or closed, and in the third operation state, the first compressor 1 and the second compressor 2 are connected in parallel to the indoor unit heat exchanger 16. In an alternative embodiment, one end of the second pipe 6 is connected to the air inlet of the first compressor 1, the other end of the second pipe 6 is connected to one end of the first pipe 3, the other end of the first pipe 3 is connected to the air inlet of the second compressor 2, one end of the fourth pipe 8 is connected to the air outlet of the second compressor 2, and the other end of the fourth pipe 8 is connected to the second pipe 6; the first pipeline 3 and the third pipeline 7 are used for communicating with the indoor unit heat exchanger 16; in the air conditioner 100 in the first operation state, the first valve body 4 and the second valve body 5 are both in an open state, the air inlet of the second compressor 2, the air outlet of the second compressor 2, the fourth pipeline 8 and the first pipeline 3 are communicated in a closed loop manner to form a first refrigerant circulation flow path, and the air inlet of the second compressor 2, the air outlet of the second compressor 2, the fourth pipeline 8, the second pipeline 6, the air inlet of the first compressor 1, the air outlet of the first compressor 1, the third pipeline 7, the indoor unit heat exchanger and the first pipeline 3 are communicated in a closed loop manner to form a second refrigerant circulation flow path; in the second operation state of the air conditioner 100, the first valve body 4 is in a closed state, the second valve body 5 is in an open state, and the air inlet of the second compressor 2, the air outlet of the second compressor 2, the fourth pipeline 8, the second pipeline 6, the air inlet of the first compressor 1, the air outlet of the first compressor 1, the third pipeline 7, the indoor unit heat exchanger and the first pipeline 3 are in closed-loop communication to form a refrigerant circulation flow path; in the third operation state of the air conditioner 100, the first valve body 4 is in an open state, the second valve body 5 is in a closed state, and the first compressor 1 and the second compressor 2 are connected in parallel.
According to the application, the first valve body 4 and the second valve body 5 are arranged, so that the air conditioner 100 has three operation states in heating operation, and therefore, the air conditioner 100 can be selected according to different use environments and use requirements when the air conditioner 100 is used, and the heating effect of the air conditioner 100 is better, and the air conditioner is more convenient to use and saves energy.
In the present embodiment, the second valve body 5 is also a solenoid valve, but in other embodiments of the present application, the second valve body 5 may be another type of electrically controlled valve.
In this embodiment, the air conditioner 100 further includes a reverse pressure flow valve 9, the reverse pressure flow valve 9 is disposed in the first pipe 3, the reverse pressure flow valve 9 is used for limiting the flow of the refrigerant in the first operation state, so that part of the refrigerant discharged from the discharge port of the second compressor 2 flows to the discharge port of the first compressor 1, the other part flows to the air inlet of the second compressor 2, and the reverse pressure flow valve 9 is also used in the third operation state, to make the first pipe 3 conductive and make part of the refrigerant flow to the air inlet of the first compressor 1.
Referring to fig. 6, in the embodiment, the reverse pressure flow valve 9 includes a valve seat 91 and a valve core 92, the valve core 92 is movably installed in the valve seat 91, a first flow channel 93 is formed between a side wall of the valve core 92 and a side wall of the valve seat 91, the valve core 92 is provided with a second flow channel 94, the diameter of the second flow channel 94 is relatively smaller, in the first operation state, since one side of the reverse pressure flow valve 9 is a high pressure refrigerant and the other side is a low pressure refrigerant, so that pressure difference is formed on two sides of the valve core 92, the valve core 92 moves under the action of the pressure difference, so that the first flow channel 93 is closed by the valve core 92, at this time, a part of refrigerant flowing out from an exhaust port of the second compressor 2 flows to an air inlet of the first compressor 1, and the other part of refrigerant flowing from the second flow channel 94 to the air inlet of the second compressor 2 forms a second refrigerant circulation loop, so that the first refrigerant circulation loop and the second refrigerant circulation loop are performed simultaneously. In the second operation state, the first compressor 1 and the second compressor 2 are connected in parallel, so that the refrigerant pushes the valve core 92, the valve core 92 can open the first flow channel 93, and at this time, the refrigerant can flow to the air inlet of the first compressor 1 through the first flow channel 93 and the second flow channel together, so that different flow rates are realized when the refrigerant flows in two opposite directions.
By providing the reverse pressure flow valve 9, the refrigerant can be restricted when the air conditioner 100 is operated in the first operation state, and a part of the refrigerant flowing out of the second compression exhaust port flows to the air inlet of the first compressor 1, and the other part flows to the air inlet of the second compressor 2, so that the normal operation of the first refrigerant circulation flow path and the second refrigerant circulation flow path is ensured. In the third operating state, the refrigerant can flow to the inlet of the first compressor 1 at a large flow rate.
In the present embodiment, the air conditioner 100 further includes a check valve 10, the check valve 10 being mounted to the third duct 7, the check valve 10 being for blocking the third duct 7 in the first operation state and the second operation state, the check valve 10 being further for making the third duct 7 conductive in the third operation state. The provision of the non-return valve 10 makes it possible to block the third conduit 7 in the first operating state and in the second operating state, and to put the third conduit 7 in communication with a large flow in the third operating state.
In the present embodiment, the structure of the check valve 10 and the check valve 9 is substantially the same, except that the spool 92 of the check valve 9 has no second flow passage 94. In the first operation state or the second operation state of the air conditioner 100, the valve core 92 moves due to the pressure difference across the check valve 10, so that the refrigerant flowing out of the outlet of the second compressor 2 can flow into the first pipe 3 entirely. When the air conditioner 100 is operated in the third operation state, the pressure difference across the back pressure valve is substantially the same, so that the valve core 92 can open the flow passage to allow the refrigerant discharged from the outlet of the second compressor 2 to flow into the third pipe 7.
In the present embodiment, the air conditioner 100 further includes a four-way valve 11, a fifth pipe 12, a sixth pipe 13, an outdoor unit heat exchanger 14, an outdoor unit expansion valve 15, and an indoor unit heat exchanger 16; one end of the fifth pipeline 12 is connected with the third pipeline 7, so that the refrigerant flowing out of the exhaust port of the first compressor 1 and/or the refrigerant flowing out of the exhaust port of the second compressor 2 can flow into the fifth pipeline 12, the other end of the fifth pipeline 12 is communicated with the first interface of the four-way valve 11, one end of the sixth pipeline 13 is connected with the first pipeline 3, the other end is communicated with the third interface of the four-way valve 11, one end of the outdoor unit heat exchanger 14 is communicated with the second interface of the four-way valve 11, the other end is communicated with the outdoor unit expansion valve 15, one end of the indoor unit heat exchanger 16 is communicated with the outdoor unit expansion valve 15, and the other end is communicated with the fourth interface of the four-way valve 11. The four-way valve 11 is provided to regulate the flow direction of the refrigerant in consideration of the cooling and heating requirements of the air conditioner 100.
In this embodiment, the air conditioner 100 is a multi-connected air conditioner 100, i.e. a plurality of indoor units corresponds to one outdoor unit. The air conditioner 100 further includes an indoor unit expansion valve 20, and the indoor unit expansion valve 20 is connected in series between the indoor unit heat exchanger and the outdoor expansion valve; in other embodiments of the present application, the air conditioner 100 may be a conventional one-to-one air conditioner 100.
In this embodiment, the air conditioner 100 further includes an auxiliary heat exchange assembly 17, a third valve body 18 and a seventh pipe 19, the auxiliary heat exchange assembly 17 is connected between the outdoor unit expansion valve 15 and the indoor unit expansion valve 20, the auxiliary heat exchange assembly 17 is communicated with the fourth pipe 8, one end of the seventh pipe 19 is connected with the fourth pipe 8, the other end is connected with the first pipe 3, the third valve body 18 is disposed in the seventh pipe 19, and the third valve body 18 is used for controlling on-off of the seventh pipe 19; in the third operating state, the first valve body 4 is in an open state, the second valve body 5 is in a closed state, the third valve body 18 is in an open state, and the auxiliary heat exchange assembly 17 can convey the heat exchanged refrigerant to the air inlet of the first compressor 1 and the air inlet of the second compressor 2. The third valve body 18 and the auxiliary heat exchange assembly 17 are arranged to recycle and reuse energy, so that the energy consumption of the air conditioner 100 is reduced.
In the present embodiment, the auxiliary heat exchange unit 17 includes an auxiliary heat exchanger 171 and an auxiliary heat exchange expansion valve 172, the auxiliary heat exchanger 171 is connected between the outdoor unit expansion valve 15 and the indoor unit expansion valve 20, one end of the auxiliary heat exchanger 171 is in communication with the auxiliary heat exchanger 171, the other end is in communication with the outdoor expansion valve, and the auxiliary heat exchanger 171 is in communication with the fourth pipe 8. Heat recovery can be performed in the heating operation by providing the auxiliary heat exchanger 171 and the auxiliary heat exchanger 171 expansion valve. In the third operating state, the third valve body 18 and the auxiliary heat exchange expansion valve 172 are opened, and the refrigerant heated by the auxiliary heat exchanger 171 can be introduced into the intake port of the first compressor 1 and the intake port of the second compressor 2.
Referring to fig. 7, an embodiment of the present application further provides a control method of the air conditioner 100 for the air conditioner 100, where the control method includes:
s1, acquiring outdoor environment temperature;
s2, judging whether the outdoor environment temperature is lower than a preset outdoor environment temperature or not under the condition that a heating instruction is received;
s3, judging whether the outdoor environment temperature is lower than the preset outdoor environment temperature, if so, configuring starting operation parameters of the air conditioner 100, controlling the first valve body 4 and the second valve body 5 to be opened, controlling the first interface and the fourth interface of the four-way valve 11 to be communicated, and controlling the air conditioner 100 to start operation according to the first operation state.
The control method of the air conditioner 100 of the application judges whether the outdoor environment temperature is lower than the preset outdoor environment temperature under the condition of receiving the heating instruction, configures the starting operation parameters of the air conditioner 100 when the outdoor environment temperature is lower than the preset outdoor environment temperature, controls the first valve body 4 and the second valve body 5 to be opened, controls the first interface and the fourth interface of the four-way valve 11 to be communicated, and controls the air conditioner 100 to operate according to the first operation state, so that the air conditioner 100 is provided with a first refrigerant circulation flow path and a second refrigerant circulation flow path which are simultaneously operated when the air conditioner is started for heating, wherein the air inlet of the second compressor 2 in the first refrigerant circulation flow path, the air outlet of the second compressor 2 and the first pipeline 3 are communicated in a closed loop, and the air inlet of the second compressor 2, the air outlet of the first compressor 1 and the indoor unit heat exchanger 16 are communicated in a closed loop. Therefore, the second refrigerant circulation flow path can maintain the normal heating cycle of the indoor unit. Meanwhile, the temperature of the refrigerant at the air inlet of the second compressor 2 can be increased by utilizing the first refrigerant circulation flow path to lead the refrigerant compressed by the second compressor 2 into the second compressor 2 through the first pipeline 3, so that the temperature of the refrigerant in the refrigerant loop is increased, and the starting time of the air conditioner 100 during heating and starting can be shortened.
In this example, the preset ambient temperature is-5 ℃. Of course, in other embodiments of the present application, the preset ambient temperature may be-10 ℃, or the preset ambient temperature may be set and adjusted according to the temperature of the region where the present application is actually used. It is understood that the embodiment of the present application is not limited to the temperature value of the preset ambient temperature.
In this embodiment, the step of configuring the start-up operation parameters of the air conditioner 100 includes:
s31, controlling the starting frequency of the first compressor 1 to be one half of the rated starting frequency of the first compressor 1; controlling the starting frequency of the second compressor 2 to be twice the starting frequency of the first compressor 1; controlling the opening degree of the outdoor unit expansion valve 15 to be the minimum opening degree; controlling the outdoor unit expansion valve 15 to be at a minimum opening; the heat-assisted heat exchange expansion valve 172 is controlled to be fully closed.
The application can adjust the circulation quantity of the first compressor 1 and the second compressor 2 by setting the starting frequency of the first compressor 1 to be one half of the rated starting frequency of the first compressor 1, setting the starting frequency of the second compressor 2 to be twice the starting frequency of the first compressor 1 and setting the opening degree of the outdoor unit expansion valve 15 to be the lowest opening degree, and can adjust the medium pressure to be the pressure with the highest operation efficiency.
In this embodiment, after the step of controlling the air conditioner 100 to operate in the first operation state, the control method further includes:
s4, obtaining the superheat degree of the exhaust port of the second compressor 2 and the superheat degree of the air inlet of the first compressor 1;
s5, judging whether the superheat degree of the exhaust port of the first compressor 1 is larger than a preset exhaust heat degree and whether the superheat degree of the air inlet of the second compressor 2 is larger than a preset suction superheat degree;
and S6, if the superheat degree of the exhaust port of the first compressor 1 is larger than the preset exhaust heat degree and the superheat degree of the air inlet of the second compressor 2 is larger than the preset suction superheat degree, controlling the air conditioner 100 to perform heating operation in the second operation state or the third operation state.
The application can conveniently judge whether the air conditioner 100 is started to be finished or not through the superheat degree of the exhaust port of the first compressor 1 and the superheat degree of the air inlet of the second compressor 2, and after the air conditioner 100 is started to be finished, the air conditioner 100 is controlled to operate in the second operation state or the third operation state, so that the heating operation effect of the air conditioner 100 is good, and meanwhile, the operation of the air conditioner 100 is more energy-saving.
In this embodiment, the preset exhaust superheat degree is 10k, and the preset suction superheat degree is 3k. Of course, in other embodiments of the present application, the preset discharge superheat degree and the preset suction superheat degree may be set according to the type of the compressor and the use environment.
Referring to fig. 8, in the present embodiment, the step of controlling the air conditioner 100 to perform the heating operation in the second operation state or the third operation state includes:
s61 obtains low pressure values of the first compressor 1 and the second compressor 2, and/or obtains compression ratios of the first compressor 1 and the second compressor 2;
s62, judging whether the low pressure values of the first compressor 1 and the second compressor 2 are smaller than a preset low pressure value or judging whether the compression ratio of the first compressor 1 and the second compressor 2 is larger than a preset compression ratio;
if the low pressure value of the first compressor 1 and the second compressor 2 is smaller than the preset low pressure value or the compression ratio of the first compressor 1 and the second compressor 2 is larger than the preset compression ratio, the first valve body 4 is controlled to be closed and the second valve body 5 is controlled to be opened, the operation parameters of the second operation state of the air conditioner 100 are configured, and the air conditioner 100 is controlled to operate in the second operation state.
In this embodiment, the preset low pressure value is 0.6Mpa (g) and the preset compression ratio is 2.0. Of course, in other embodiments of the present application, the preset low pressure value and the preset compression ratio may also be selected according to the type of compressor and the place of use.
According to the low-pressure value of the first compressor 1 and the second compressor 2 or the compression ratio of the first compressor 1 and the second compressor 2, the air conditioner can be conveniently controlled to operate in the second operation state or the third operation state by the air conditioner, so that the air conditioner 100 has pertinence with the environment, and the use of the air conditioner 100 is more energy-saving.
In the present embodiment, the step of controlling the air conditioner 100 to perform the heating operation in the second operation state or the third operation state further includes:
if the low pressure value of the first compressor 1 and the second compressor 2 is greater than or equal to the preset low pressure value or the compression ratio of the first compressor 1 and the second compressor 2 is less than or equal to the preset compression ratio, S64 controls the first valve body 4 to open and the second valve body 5 to close, configures the operation parameters of the third operation state of the air conditioner 100, and controls the air conditioner 100 to operate in the third operation state.
According to the low-pressure value of the first compressor 1 and the second compressor 2 or the compression ratio of the first compressor 1 and the second compressor 2, the air conditioner can be conveniently controlled to operate in the second operation state or the third operation state by the air conditioner, so that the air conditioner 100 has pertinence with the environment, and the use of the air conditioner 100 is more energy-saving.
Referring to fig. 9, the steps of configuring the operation parameters of the second operation state of the air conditioner 100 are as follows:
s631, acquiring the air inlet pressure of the second compressor 2 at the current moment, acquiring the air outlet pressure of the first compressor 1 at the current moment, acquiring the superheat degree of the outlet of the outdoor unit heat exchanger 14 at the current moment, acquiring the opening degree of the outdoor unit expansion valve 15 at the current moment, and acquiring the current opening degree of the indoor unit expansion valve and the supercooling degree of the outlet of the indoor unit heat exchanger;
S632 calculates the medium pressure according to the following formula:
P m ＝(P h *P s )^(1/2)；
P m represents the medium pressure, P h Represents the discharge pressure, P, of the first compressor 1 s Representing the second compressor 2 inlet pressure;
s633, determining a first refrigerant density corresponding to the medium pressure and a second refrigerant density corresponding to the air inlet pressure of the second compressor 2 according to the refrigerant physical property table;
specifically, the first refrigerant density and the second refrigerant density are both related to the ambient temperature T and the pressure P, the first refrigerant density corresponds to the vapor density, and the second refrigerant density corresponds to the liquid density. Specifically, the refrigerant can be searched according to a refrigerant physical property table.
The following is a partial refrigerant physical property table of the R32 type refrigerant:
temperature T (. Degree. C.) Pressure P (Mpa) Density of liquid (Kg/m) 3 ) Density of steam (Kg/m) 3 )
-35 0.22138 1165.3 6.2476
-20 0.40575 1120.6 11.157
-5 0.69058 1072.2 18.769
5 0.95145 1037.7 25.891
20 1.4746 981.38 40.856
35 2.1898 917.05 63.343
The following is a partial refrigerant physical property table of the R410A type refrigerant:
s634 calculates the operating frequency of the second compressor 2 at the next moment according to the following formula:
H zs(t+1) ＝H zs(t+1) *(ρ m /ρ s )/(1+α)；
H zs(t+1) indicating the operating frequency ρ of the second compressor 2 at the next time h Represents the first refrigerant density ρ s The density of the second refrigerant is represented, alpha represents the cycle ratio of the spray enthalpy, and the value of alpha is 0.15-0.30;
s635 controls the next time of the second compressor 2 to H zs(t+1) Is a frequency operation of (2);
s636 calculates the frequency adjustment value of the first compressor 1 according to the following formula:
△H zh ＝fx(P g -P h )；
△H zh Represents the frequency adjustment value, P, of the first compressor 1 g Representing the target pressure, P h Represents the discharge port pressure of the first compressor 1;
s638 calculates the operation frequency of the first compressor 1 at the next time according to the following formula:
H zh(t+1) ＝H zh(t) +△H z ；
H zh(t+1) indicating the operating frequency H of the first compressor 1 at the next moment zh(t) The operation frequency of the first compressor 1 at this time is shown;
s639 controls the first compressor 1 to be at the next time to be H zh(t+1) Is a frequency operation of (2);
s6310 calculates an adjustment value of the opening degree of the outdoor expansion valve 15 according to the following formula:
△P ls ＝g x (S HG –S H )；
Δpls represents the opening adjustment value of the outdoor unit expansion valve 15, SHG represents the target superheat degree, and SH represents the superheat degree of the outlet of the outdoor unit heat exchanger 14;
s6311 calculates the opening of the outdoor expansion valve 15 at the next moment according to the following formula;
Pls(t+1)＝Pls(t)+△Pls；
P ls(t+1) indicating the opening degree P of the outdoor unit expansion valve 15 at the next moment ls(t) The opening degree of the outdoor unit expansion valve 15 at the current time;
s6312 controlling the next time P of the outdoor expansion valve 15 ls(t+1) Opening degree operation;
s6313 calculates an adjustment value of the opening degree of the indoor-unit expansion valve 20 according to the following formula:
△P lsc ＝K x (S cG –S c )；
Δplsc represents the opening adjustment value of the indoor expansion valve 20, scG represents the target supercooling degree, SH represents the outdoor heat exchanger 14 outlet supercooling degree;
s6314, calculating the opening of the indoor unit expansion valve 20 at the next moment according to the following formula;
P lsc(t+1) ＝P lsc(t) +△P lsc ；
P lsc(t+1) Indicating the opening degree P of the indoor unit expansion valve 20 at the next moment lsc(t) Indicating the opening of the indoor expansion valve 20 at the current time;
s6315 controls the indoor-unit expansion valve 20 to operate at the opening degree Pls (t+1) at the next timing.
In this embodiment, the step of configuring the operation parameters of the second operation state of the air conditioner 100 further includes:
s6316 calculates an adjustment value of the opening degree of the auxiliary heat exchange expansion valve 172 according to the following formula:
△P lsf ＝gx(S Hf –S f )；
△P lsf represents the opening adjustment value of the auxiliary heat exchange expansion valve 172, S Hf Indicating the target superheat degree S f Indicating the superheat degree of the outlet of the heat assist heater;
s6317, calculating the opening of the auxiliary heat exchange expansion valve 172 at the next moment according to the following formula;
P lsf (t+1)＝P lsf (t)+△P lsf ；
P lsf(t+1) represents the opening degree, P, of the auxiliary heat exchange expansion valve 172 at the next time lsf(t) The opening degree of the auxiliary heat exchange expansion valve 172 at the present time;
s6318 controlling the opening of the auxiliary heat exchange expansion valve 172 to be P at the next moment ls(t+1) And (5) opening operation.
In the second operation state, the operation parameters of the air conditioner 100 are adjusted, so that the operation state and the operation parameters of the air conditioner 100 can be matched, and the heating operation effect of the air conditioner 100 is better.
In this embodiment, the step of controlling the air conditioner 100 to operate in the second operation state further includes:
S6319 determines whether or not the air conditioner 100 has received the heating operation stop instruction;
s6319, if the air conditioner 100 receives the heating operation stop instruction, controlling the air conditioner 100 to stop the heating operation;
if the air conditioner 100 does not receive the heating operation stop command, the steps S631 to S6318 are looped, and the steps S631 to S6317 are performed simultaneously.
Referring to fig. 10, in the present embodiment, the step of configuring the operation parameters of the third operation state of the air conditioner 100 includes:
s641 obtains the exhaust port pressure of the first compressor 1 and the second compressor 2, the operating frequency of the first compressor 1 and the second compressor 2 and the superheat degree of the outlet of the outdoor heat exchanger 14 at the current moment, the opening degree of the outdoor expansion valve 15 at the current moment, the current opening degree of the indoor expansion valve and the supercooling degree of the outlet of the indoor heat exchanger;
s642 calculates the frequency adjustment values of the first compressor 1 and the second compressor 2 according to the following formula:
△H z ＝fx(P g -P h )；
Δhz represents the frequency adjustment values of the first compressor 1 and the second compressor 2, pg represents the target pressure, and Ph represents the discharge pressure of the first compressor 1 or the discharge pressure of the second compressor 2;
s643 calculates the operation frequencies of the first compressor 1 and the second compressor 2 at the next time according to the following formula:
Hz (t+1) ＝Hz (t) +△Hz；
Hz (t+1) Indicating the operating frequency, hz, of the first compressor 1 and the second compressor 2 at the next moment (t) Indicating the operating frequencies of the first compressor 1 and the second compressor 2 at the present moment;
s644 controls the first compressor 1 and the second compressor 2 to be at Hz at the next time (t+1) Frequency operation;
s645 calculates the adjustment value of the opening degree of the outdoor expansion valve 15 according to the following formula:
△P ls ＝g x (S HG –S H )；
△P ls represents the opening adjustment value of the expansion valve 15 of the outdoor unit, S HG Indicating the target superheat degree S H Indicating the superheat degree of the outlet of the heat exchanger 14 of the outdoor unit;
s646 calculates the opening of the outdoor expansion valve 15 at the next moment according to the following formula;
P ls(t+1) ＝P ls(t) +△P ls ；
P ls(t+1) indicating the opening degree P of the outdoor unit expansion valve 15 at the next moment ls(t) The opening degree of the outdoor unit expansion valve 15 at the current time;
s647 controls the next time P of the outdoor expansion valve 15 ls(t+1) Opening degree operation;
s648 calculates the opening adjustment value of the indoor expansion valve 20 according to the following formula:
△P lsc ＝k x (S cG –S c )；
Δplsc represents the opening adjustment value of the indoor expansion valve 20, scG represents the target supercooling degree, SH represents the outdoor heat exchanger 14 outlet supercooling degree;
s649 calculates the opening of the indoor unit expansion valve 20 at the next time according to the following formula:
P lsc(t+1) ＝P lsc(t) +△P lsc ；
P lsc(t+1) indicating the opening degree P of the indoor unit expansion valve 20 at the next moment lsc(t) Indicating the opening of the indoor expansion valve 20 at the current time;
S6410 controlling the indoor unit expansion valve 20 to be P at the next time ls(t+1) And (5) opening operation.
In the present embodiment, the step of controlling the air conditioner 100 to operate in the third operation state includes:
s6411, judging whether the air conditioner 100 receives a heating operation stop instruction;
s6412, if the air conditioner 100 receives the heating operation stop command, the air conditioner 100 is controlled to stop the heating operation, and if the air conditioner 100 does not receive the heating operation stop command, the steps S641 to S6410 are looped, and the steps S641 to S6410 are simultaneously performed.
In the third operation state, the operation parameters of the air conditioner 100 are adjusted, so that the operation state and the operation parameters of the air conditioner 100 can be matched, and the heating operation effect of the air conditioner 100 is better.
Referring to fig. 5, 11 and 12, in the present embodiment, when the air conditioner 100 receives a cooling command, the control method includes:
s101, controlling the first interface and the second interface of the four-way valve 11 to be communicated;
s102, controlling the first valve body 4 to be opened, the second valve body 5 to be closed and the outdoor unit expansion valve 15 to be fully opened;
s103, configuring refrigeration operation parameters;
s104 controls the air conditioner 100 to perform a cooling operation.
When receiving a refrigeration instruction, the air conditioner 100 of the application controls the first valve body 4 to be opened and the second valve body 5 to be closed, so that the first compressor 1 and the second compressor 2 are connected in series, and the refrigeration effect of the air conditioner 100 is better.
In an embodiment, the step of configuring the refrigeration operating parameter comprises:
s1031, acquiring inlet pressures of the first compressor 1 and the second compressor 2 at the current moment and running frequencies of the first compressor 1 and the second compressor 2 at the current moment;
s1032 calculates the frequency adjustment values of the first compressor 1 and the second compressor 2 according to the following formula:
△Hz＝f x (P g -P s )；
Δhz represents the frequency adjustment values of the first compressor 1 and the second compressor 2, P g Representing the target pressure, P s Represents the inlet pressure of the first compressor 1 or the inlet pressure of the second compressor 2;
s1033 calculates the operation frequencies of the first compressor 1 and the second compressor 2 at the next time according to the following formula: hz (Hz) (t+1) ＝Hz (t) +△Hz；
Hz (t+1) Indicating the operating frequency, hz, of the first compressor 1 and the second compressor 2 at the next moment (t) Indicating the operating frequencies of the first compressor 1 and the second compressor 2 at the present moment;
s1034 controls the first compressor 1 and the second compressor 2 at the next time in Hz (t+1) Frequency operation.
S1035 calculates an adjustment value of the opening degree of the indoor unit expansion valve 20 according to the following formula:
△P lsc ＝g x (S hG –S c )；
△P lsc s represents the opening adjustment value of the expansion valve 20 of the indoor unit cG Indicating the target supercooling degree S c Indicating the degree of supercooling at the outlet of the outdoor heat exchanger 14;
s1036, calculating the opening of the indoor unit expansion valve 20 at the next moment according to the following formula;
P lsc(t+1) ＝P lsc(t) +△P lsc ；
P lsc(t+1) Indicating the opening degree P of the indoor unit expansion valve 20 at the next moment lsc(t) Indicating the opening of the indoor expansion valve 20 at the current time;
s1037 controls the indoor unit expansion valve 20 to take P at the next moment ls(t+1) And (5) opening operation.
The application configures the parameters of the air conditioner 100 during the refrigeration operation, so that the operation parameters and the operation conditions of the air conditioner 100 during the refrigeration operation are more matched, and the refrigeration effect of the air conditioner 100 is better.
In the present embodiment, the step of controlling the air conditioner 100 to perform the cooling operation includes:
s1041, judging whether the air conditioner 100 receives a cooling operation stop command;
s1042 controls the air conditioner 100 to stop the heating operation when the air conditioner 100 receives the cooling operation stop command, and if the air conditioner 100 does not receive the cooling operation stop command, the steps S631 to S6317 are repeated, and the steps S1031 to S1037 are performed simultaneously.
The working principle and beneficial effects of the air conditioner 100 and the control method of the air conditioner 100 provided by the embodiment of the application include:
the application connects the first compressor 1 and the second compressor 2 in series, and connects the exhaust port and the air inlet of the second compressor 2 through the first pipeline 3, thereby having a first refrigerant circulation flow path and a second refrigerant circulation flow path which run simultaneously when the air device is heated and started, wherein the air inlet of the second compressor 2 in the first refrigerant circulation flow path, the exhaust port of the second compressor 2 and the first pipeline 3 are communicated in a closed loop, and the air inlet of the second compressor 2, the exhaust port of the second compressor 2, the air inlet of the first compressor 1, the exhaust port of the first compressor 1 and the indoor unit heat exchanger 16 are communicated in a closed loop. Therefore, the second refrigerant circulation flow path can maintain the normal heating cycle of the indoor unit. Meanwhile, the temperature of the refrigerant at the air inlet of the second compressor 2 can be increased by utilizing the first refrigerant circulation flow path to lead the refrigerant compressed by the second compressor 2 into the second compressor 2 through the first pipeline 3, so that the temperature of the refrigerant in the refrigerant loop is increased, and the starting time of the air conditioner 100 during heating and starting can be shortened.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be made by one skilled in the art without departing from the spirit and scope of the invention, and the scope of the invention should be assessed accordingly to that of the appended claims.

Claims (12)

1. An air conditioner characterized in that the air conditioner (100) comprises a first compressor (1), a second compressor (2), a first pipeline (3), a second valve body (5), a second pipeline (6), a third pipeline (7) and a fourth pipeline (8);
one end of the second pipeline (6) is connected with the air inlet of the first compressor (1), the other end of the second pipeline (6) is connected with one end of the first pipeline (3), the other end of the first pipeline (3) is connected with the air inlet of the second compressor (2), one end of the fourth pipeline (8) is connected with the air outlet of the second compressor (2), and the other end of the fourth pipeline (8) is connected with the second pipeline (6); the second pipeline (6), the first pipeline (3) and the third pipeline (7) are used for being communicated with an indoor unit heat exchanger (16); the exhaust port of the second compressor (2) is communicated with the air inlet of the first compressor (1), and the exhaust port of the second compressor (2) is communicated with the air inlet of the second compressor (2) through the first pipeline (3) and the fourth pipeline; the exhaust port of the first compressor (1) and the air inlet of the second compressor (2) are connected with an indoor unit heat exchanger (16);
The air conditioner (100) is provided with a first refrigerant circulation flow path and a second refrigerant circulation flow path which are operated simultaneously in an operation state, wherein an air inlet of the second compressor (2), an air outlet of the second compressor (2), the fourth pipeline and the first pipeline (3) in the first refrigerant circulation flow path are communicated in a closed loop manner, and an air inlet of the second compressor (2), an air outlet of the second compressor (2), an air inlet of the first compressor (1), an air outlet of the first compressor (1) and the indoor unit heat exchanger (16) in the second refrigerant circulation flow path are communicated in a closed loop manner;
the air conditioner (100) further comprises a first valve body (4), the first valve body (4) is arranged on the first pipeline (3), and the first valve body (4) is used for controlling the on-off of the first pipeline (3);
the air conditioner (100) has a first operation state in which the first valve body (4) is opened, and in the first operation state, the first refrigerant circulation flow path and the second refrigerant circulation flow path are operated simultaneously;
the air conditioner (100) also has a second operation state in which the first valve body (4) is closed, and in the second operation state, the air inlet of the second compressor (2), the air outlet of the second compressor (2), the air inlet of the first compressor (1), the air outlet of the first compressor (1) and the indoor unit heat exchanger are communicated in a closed loop;
The air inlet of the first compressor (1) is communicated with the air inlet of the second compressor (2) through the second pipeline (6) and the first pipeline; the exhaust port of the second compressor (2) is communicated with the exhaust port of the first compressor (1) through the third pipeline (7);
the exhaust port of the second compressor (2) is communicated with the air inlet of the first compressor (1) through the fourth pipeline (8) and the second pipeline;
the second valve body (5) is arranged on the fourth pipeline (8), and the second valve body (5) is used for controlling the on-off of the fourth pipeline (8);
in the first operation state, the first valve body (4) and the second valve body (5) are both in an open state, the air inlet of the second compressor (2), the air outlet of the second compressor (2), the fourth pipeline (8) and the first pipeline (3) are communicated in a closed loop manner to form a first refrigerant circulation flow path, and the air inlet of the second compressor (2), the air outlet of the second compressor (2), the fourth pipeline (8), the second pipeline (6), the air inlet of the first compressor (1), the air outlet of the first compressor (1), the third pipeline (7), the indoor unit heat exchanger and the first pipeline (3) are communicated in a closed loop manner to form a second refrigerant circulation flow path;
In the second operation state, the air conditioner (100) is in a closed state, the first valve body (4) is in an open state, the air inlet of the second compressor (2), the air outlet of the second compressor (2), the fourth pipeline (8), the second pipeline (6), the air inlet of the first compressor (1), the air outlet of the first compressor (1), the third pipeline (7), the indoor unit heat exchanger and the first pipeline (3) are communicated in a closed loop manner to form a refrigerant circulation flow path;
in a third operation state of the air conditioner (100), the first valve body (4) is in an open state, the second valve body (5) is in a closed state, and the first compressor (1) and the second compressor (2) are connected in parallel;
the air conditioner (100) further comprises a four-way valve (11), a fifth pipeline (12), a sixth pipeline (13), an outdoor unit heat exchanger (14), an outdoor unit expansion valve (15) and an indoor unit heat exchanger (16);
one end of the fifth pipeline (12) is connected with the third pipeline (7) so that the refrigerant flowing out of the exhaust port of the first compressor (1) and/or the refrigerant flowing out of the exhaust port of the second compressor (2) can flow into the fifth pipeline (12), the other end of the fifth pipeline (12) is communicated with the first interface of the four-way valve (11), one end of the sixth pipeline (13) is connected with the first pipeline (3), the other end of the sixth pipeline is communicated with the third interface of the four-way valve (11), one end of the outdoor unit heat exchanger (14) is communicated with the second interface of the four-way valve (11), the other end of the outdoor unit heat exchanger (14) is communicated with the outdoor unit expansion valve (15), and one end of the indoor unit heat exchanger (16) is communicated with the outdoor unit expansion valve (15), and the other end of the sixth pipeline (13) is communicated with the fourth interface of the four-way valve (11).
If the outdoor environment temperature is lower than the preset outdoor environment temperature under the condition that the air conditioner receives a heating instruction, the starting operation parameters of the air conditioner (100) are configured, the first valve body (4) and the second valve body (5) are controlled to be opened, the first interface and the fourth interface of the four-way valve (11) are controlled to be communicated, and the air conditioner (100) is controlled to operate according to the first operation state;
configuring the start-up operating parameters of the air conditioner (100) includes:
controlling the starting frequency of the first compressor (1) to be one half of the rated starting frequency of the first compressor (1); controlling the starting frequency of the second compressor (2) to be twice the starting frequency of the first compressor (1); and controlling the opening degree of the outdoor unit expansion valve (15) to be the lowest opening degree.
2. The air conditioner according to claim 1, wherein the air conditioner (100) further comprises a reverse pressure flow valve (9), the reverse pressure flow valve (9) is disposed on the first pipe (3), the reverse pressure flow valve (9) is used for limiting the flow of the refrigerant in the first operation state, so that the refrigerant discharged from the discharge port of the second compressor (2) flows partially to the discharge port of the first compressor (1), and the other part flows to the air inlet of the second compressor (2), and the reverse pressure flow valve (9) is further used for conducting the first pipe (3) and flowing a part of the refrigerant to the air inlet of the first compressor (1) in the third operation state.
3. An air conditioner according to claim 1, wherein the air conditioner (100) further comprises a non-return valve (10), the non-return valve (10) being mounted to the third duct (7), the non-return valve (10) being adapted to block the third duct (7) in the first and second operating states, the non-return valve (10) being further adapted to render the third duct (7) conductive in the third operating state.
4. The air conditioner according to claim 1, wherein the air conditioner (100) further comprises an auxiliary heat exchange assembly (17), a third valve body (18) and a seventh pipe (19), the auxiliary heat exchange assembly (17) is connected between the outdoor unit expansion valve (15) and the indoor unit heat exchanger (16), the auxiliary heat exchange assembly (17) is communicated with the fourth pipe (8), one end of the seventh pipe (19) is connected with the fourth pipe (8), the other end is connected with the first pipe (3), the third valve body (18) is arranged on the seventh pipe (19), and the third valve body (18) is used for controlling the on-off state of the seventh pipe (19);
in the third operation state, the first valve body (4) is in an open state, the second valve body (5) is in a closed state, the third valve body (18) is in an open state, and the auxiliary heat exchange assembly (17) can convey the heat exchanged refrigerant to the air inlet of the first compressor (1) and the air inlet of the second compressor (2).
5. An air conditioner control method, characterized by being applied to the air conditioner (100) of claim 1, comprising:
acquiring outdoor environment temperature;
judging whether the outdoor environment temperature is lower than a preset outdoor environment temperature or not under the condition of receiving a heating instruction;
if the outdoor environment temperature is lower than the preset outdoor environment temperature, configuring starting operation parameters of the air conditioner (100), controlling the first valve body (4) and the second valve body (5) to be opened, controlling the first interface and the fourth interface of the four-way valve (11) to be communicated, and controlling the air conditioner (100) to operate according to the first operation state;
the step of configuring the start-up operation parameters of the air conditioner (100) includes:
controlling the starting frequency of the first compressor (1) to be one half of the rated starting frequency of the first compressor (1);
controlling the starting frequency of the second compressor (2) to be twice the starting frequency of the first compressor (1);
and controlling the opening degree of the outdoor unit expansion valve (15) to be the lowest opening degree.
6. The air conditioner control method according to claim 5, characterized in that, after the step of controlling the air conditioner (100) to operate in the first operation state, the control method further comprises:
Acquiring the superheat degree of an exhaust port of the second compressor (2) and the superheat degree of an air inlet of the first compressor (1);
and if the superheat degree of the exhaust port of the first compressor (1) is larger than the preset exhaust heat degree and the superheat degree of the air inlet of the second compressor (2) is larger than the preset suction superheat degree, controlling the air conditioner (100) to perform heating operation in the second operation state or the third operation state.
7. The air conditioner control method according to claim 6, wherein the step of controlling the air conditioner (100) to perform heating operation in the second operation state or the third operation state includes:
-obtaining low pressure values of the first compressor (1) and the second compressor (2), and/or obtaining compression ratios of the first compressor (1) and the second compressor (2);
and if the low pressure value of the first compressor (1) and the second compressor (2) is smaller than a preset low pressure value or the compression ratio of the first compressor (1) and the second compressor (2) is larger than a preset compression ratio, controlling the first valve body (4) to be closed and the second valve body (5) to be opened, configuring the operation parameters of the second operation state of the air conditioner (100), and controlling the air conditioner (100) to operate in the second operation state.
8. The air conditioner control method according to claim 7, characterized in that the step of controlling the air conditioner (100) to perform heating operation in the second operation state or the third operation state further comprises:
and if the low pressure value of the first compressor (1) and the second compressor (2) is larger than a preset low pressure value or the compression ratio of the first compressor (1) and the second compressor (2) is smaller than a preset compression ratio, controlling the first valve body (4) to be opened and the second valve body (5) to be closed, configuring the operation parameters of the third operation state of the air conditioner (100), and controlling the air conditioner (100) to operate in the third operation state.
9. The air conditioner control method according to claim 7, wherein the air conditioner (100) further includes an indoor unit expansion valve (20) and an indoor unit heat exchanger (16), the indoor unit expansion valve (20) being connected in series between the indoor unit heat exchanger and the outdoor unit expansion valve (15);
-said step of configuring operating parameters of said second operating state of said air conditioner (100):
acquiring the air inlet pressure of the second compressor (2) at the current moment, the air outlet pressure of the first compressor (1) at the current moment, the superheat degree of the outlet of the outdoor unit heat exchanger (14) at the current moment, the opening of the outdoor unit expansion valve (15) at the current moment, the current opening of the indoor unit expansion valve and the supercooling degree of the outlet of the indoor unit heat exchanger;
The medium pressure is calculated according to the following formula:
P m =(P h *P s )^(1/2)；
P m represents the medium pressure, P h Represents the discharge pressure of the first compressor (1), P s Representing the inlet pressure of the second compressor (2);
determining a first refrigerant density corresponding to the medium pressure and a second refrigerant density corresponding to the air inlet pressure of the second compressor (2) according to a refrigerant physical property table;
the operating frequency of the second compressor (2) at the next moment is calculated according to the following formula:
Hz s(t+1) =Hz s(t+1) *(ρ m /ρ s )/（1+α）；
Hz s(t+1) representing the operating frequency ρ of the second compressor (2) at the next moment h Represents the first refrigerant density ρ s The density of the second refrigerant is represented, alpha represents the cycle ratio of the spray enthalpy, and the value of alpha is 0.15-0.30;
controlling the next moment of the second compressor (2) to be Hz s(t+1) Is a frequency operation of (2);
-calculating a frequency adjustment value of the first compressor (1) according to the following formula:
△Hz h =f x (P g -P h );
△Hz h represents the frequency adjustment value, P, of the first compressor (1) g Representing the target pressure, P h Represents the discharge port pressure of the first compressor (1);
-calculating the operating frequency of the first compressor (1) at the next moment according to the following formula:
△Hz=f x (P g -P h );
Δhz represents a frequency adjustment value, pg represents a target pressure, ph represents a discharge pressure of the first compressor (1) or a discharge pressure of the second compressor (2);
-calculating the operating frequency of the first compressor (1) at the next moment according to the following formula:
Hz h(t+1) =Hz h(t) +△Hz；
Hz h(t+1) indicating the operating frequency, hz, of the first compressor (1) at the next moment h(t) Representing the operating frequency of the first compressor (1) at the instant;
controlling the next moment of the first compressor (1) to be Hz h(t+1) Is a frequency operation of (2);
calculating an adjustment value of the opening degree of the expansion valve (15) of the outdoor unit according to the following formula:
△P ls =g x (S HG –S H )；
△P ls represents the opening degree adjustment value of the expansion valve (15) of the outdoor unit, S HG Indicating the target superheat degree S H Indicating the superheat degree of the outlet of the heat exchanger (14) of the outdoor unit;
calculating the opening degree of the outdoor unit expansion valve (15) at the next moment according to the following formula;
P ls(t+1) =P ls(t) +△P ls ；
P ls(t+1) indicating the opening degree of an outdoor unit expansion valve (15) at the next moment, P ls(t) The outdoor unit expansion indicating the current timeAn opening degree of the expansion valve (15);
controlling the next time of the outdoor unit expansion valve (15) to be P ls(t+1) Opening degree operation;
calculating an adjustment value of the opening of the indoor unit expansion valve (20) according to the following formula:
△P lsc =k x (S cG –S c )；
△P lsc s represents an opening adjustment value of an expansion valve (20) of the indoor unit cG Indicating the target supercooling degree S c Indicating the supercooling degree of the outlet of the outdoor unit heat exchanger (14);
calculating the opening of the expansion valve (20) of the indoor unit at the next moment according to the following formula;
P lsc(t+1) =P lsc(t) +△P lsc ；
P lsc(t+1) Indicating the opening degree of an indoor unit expansion valve (20) at the next moment, P lsc(t) Representing the opening degree of the indoor unit expansion valve (20) at the current moment;
controlling the next moment of the expansion valve (20) of the indoor unit to be P ls(t+1) And (5) opening operation.
10. The air conditioner control method according to claim 7, wherein the air conditioner (100) further includes an indoor unit expansion valve (20), the indoor unit expansion valve (20) being connected in series between the indoor unit heat exchanger (16) and the outdoor unit expansion valve (15);
the step of configuring the operating parameters of the third operating state of the air conditioner (100) comprises:
acquiring the exhaust port pressure of the first compressor (1) and the second compressor (2), the running frequency of the first compressor (1) and the second compressor (2) and the superheat degree of the outlet of the outdoor unit heat exchanger (14) at the current moment, and acquiring the opening degree of the outdoor unit expansion valve (15) at the current moment, the current opening degree of the indoor unit expansion valve (20) and the supercooling degree of the outlet of the indoor unit heat exchanger;
calculating the frequency adjustment values of the first compressor (1) and the second compressor (2) according to the following formula:
△Hz=f x (P g -P h )；
DeltaHz represents the frequency adjustment value, P, of the first compressor (1) and the second compressor (2) g Representing the target pressure, P h Represents the discharge pressure of the first compressor (1) or the discharge pressure of the second compressor (2);
-calculating the operating frequency of the first compressor (1) and the second compressor (2) at the next moment according to the following formula: hz (Hz) (t+1) =Hz (t) +△Hz；
Hz (t+1) Representing the operating frequency, hz, of the first compressor (1) and the second compressor (2) at the next moment (t) Representing the operating frequencies of the first compressor (1) and the second compressor (2) at the current moment;
controlling the first compressor (1) and the second compressor (2) at the next moment in Hz (t+1) Frequency operation;
calculating an adjustment value of the opening degree of the expansion valve (15) of the outdoor unit according to the following formula:
△P ls =g x (S HG –S H )；
△P ls represents the opening degree adjustment value of the expansion valve (15) of the outdoor unit, S HG Indicating the target superheat degree S H Indicating the superheat degree of the outlet of the heat exchanger (14) of the outdoor unit;
calculating the opening degree of the outdoor unit expansion valve (15) at the next moment according to the following formula;
P ls(t+1) =P ls(t) + △P ls ；
P ls(t+1) an opening degree of an outdoor expansion valve (15) at the next time is represented, and Pls (t) represents an opening degree of the outdoor expansion valve (15) at the current time;
controlling the next time of the outdoor unit expansion valve (15) to be P ls(t+1) Opening degree operation;
calculating an adjustment value of the opening of the indoor unit expansion valve (20) according to the following formula:
△P lsc =k x (S cG –S c )；
△P lsc s represents an opening adjustment value of an expansion valve (20) of the indoor unit cG Indicating the target supercooling degree S H Indicating the supercooling degree of the outlet of the outdoor unit heat exchanger (14);
calculating the opening of the expansion valve (20) of the indoor unit at the next moment according to the following formula;
P lsc(t+1) =P lsc(t) + △P lsc ；
P lsc(t+1) indicating the opening degree of an indoor unit expansion valve (20) at the next moment, P lsc(t) Representing the opening degree of the indoor unit expansion valve (20) at the current moment;
controlling the next moment of the expansion valve (20) of the indoor unit to be P ls(t+1) And (5) opening operation.
11. The air conditioner control method according to claim 5, characterized in that when the air conditioner (100) receives a cooling instruction, the control method includes:
the first interface and the second interface of the four-way valve (11) are controlled to be communicated;
-making said first valve body (4) open and said second valve body (5) closed;
configuring refrigeration operation parameters;
the air conditioner (100) is controlled to perform a cooling operation.
12. The method of controlling an air conditioner according to claim 11, wherein the configuring of the cooling operation parameter includes:
acquiring the air inlet pressure of the first compressor (1) and the air inlet pressure of the second compressor (2) at the current moment and the running frequency of the first compressor (1) and the running frequency of the second compressor (2) at the current moment;
Calculating the frequency adjustment values of the first compressor (1) and the second compressor (2) according to the following formula:
△Hz=f x (P g -P s )；
DeltaHz represents the frequency adjustment value, P, of the first compressor (1) and the second compressor (2) g Representing the target pressure, P s Representing the inlet pressure of the first compressor (1) or the inlet pressure of the second compressor (2);
-calculating the operating frequency of the first compressor (1) and the second compressor (2) at the next moment according to the following formula:
Hz (t+1) =Hz (t) +△Hz；
Hz (t+1) representing the operating frequency, hz, of the first compressor (1) and the second compressor (2) at the next moment (t) Representing the operating frequencies of the first compressor (1) and the second compressor (2) at the current moment;
controlling the first compressor (1) and the second compressor (2) at the next moment in Hz (t+1) Frequency operation.
CN202210089907.4A 2022-01-25 2022-01-25 Air conditioner and control method thereof Active CN114484618B (en)

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CN112066458A (en) * 2020-09-07 2020-12-11 珠海格力电器股份有限公司 Air conditioning unit adopting throttle valve and control method thereof
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JP2005257203A (en) * 2004-03-12 2005-09-22 Tgk Co Ltd Expander
JP2006029604A (en) * 2004-07-12 2006-02-02 Matsushita Electric Ind Co Ltd Air conditioner
JP2006316852A (en) * 2005-05-11 2006-11-24 Saginomiya Seisakusho Inc Pilot operated solenoid valve and heat exchange system using the same
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