CN112268379A - Heat pump system, control method and device thereof, air conditioning equipment and storage medium - Google Patents

Heat pump system, control method and device thereof, air conditioning equipment and storage medium Download PDF

Info

Publication number
CN112268379A
CN112268379A CN202011297020.1A CN202011297020A CN112268379A CN 112268379 A CN112268379 A CN 112268379A CN 202011297020 A CN202011297020 A CN 202011297020A CN 112268379 A CN112268379 A CN 112268379A
Authority
CN
China
Prior art keywords
heat exchanger
port
pump system
outdoor heat
heat pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202011297020.1A
Other languages
Chinese (zh)
Inventor
杨智峰
戴永福
熊俊峰
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to CN202011297020.1A priority Critical patent/CN112268379A/en
Publication of CN112268379A publication Critical patent/CN112268379A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F24F1/0003—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station characterised by a split arrangement, wherein parts of the air-conditioning system, e.g. evaporator and condenser, are in separately located units
    • 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
    • F24F11/62—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
    • F24F11/65—Electronic processing for selecting an operating mode
    • 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
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • 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
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Abstract

The invention discloses a heat pump system, a control method and a control device thereof, air conditioning equipment and a storage medium. The heat pump system comprises a compressor, an indoor heat exchanger, a first outdoor heat exchanger, a second outdoor heat exchanger and a valve assembly, wherein the valve assembly is respectively connected with an air exhaust port and an air suction port of the compressor, a first end of the indoor heat exchanger, a first end of the first outdoor heat exchanger and a first end of the second outdoor heat exchanger, a second end of the indoor heat exchanger is connected with a second end of the first outdoor heat exchanger and a second end of the second outdoor heat exchanger through a first connecting pipeline, the valve assembly is configured to control one of the first outdoor heat exchanger and the second outdoor heat exchanger and the indoor heat exchanger to be in a first state, and the other of the first outdoor heat exchanger and the second outdoor heat exchanger is in a second state. Part of the refrigerant output by the compressor can be distributed to the outdoor heat exchanger, and the heat pump system can still accurately control the indoor temperature when the heat pump system approaches the load zero point.

Description

Heat pump system, control method and device thereof, air conditioning equipment and storage medium
Technical Field
The invention relates to the technical field of air conditioners, in particular to a heat pump system, a control method and a control device of the heat pump system, an air conditioner device and a storage medium.
Background
As shown in fig. 1, the conventional heat pump system includes a compressor 1a, a four-way valve 3a, an indoor heat exchanger 9a, and an outdoor heat exchanger 20 a. A first end D of the four-way valve 3a is connected to an exhaust port of the compressor 1a, a second end E of the four-way valve 3a is connected to the indoor heat exchanger 9a, a third end C of the four-way valve 3a is connected to the outdoor heat exchanger 20a, and a fourth end S of the four-way valve 3a is connected to a suction port of the compressor 1 a. When the heat pump system is in a heating mode, the four-way valve 3a is powered on, at the moment, the first end D is communicated with the second end E, the third end C is communicated with the fourth end S, the indoor heat exchanger 9a works in a condensation state, and the outdoor heat exchanger 20a works in an evaporation state. When the heat pump system is in a refrigeration mode, the four-way valve 3a is powered off, at the moment, the first end D is communicated with the third end C, the second end E is communicated with the fourth end S, the indoor heat exchanger 9a works in an evaporation state, and the outdoor heat exchanger 20a works in a condensation state. In the conventional heat pump system, the indoor heat exchanger 9a and the outdoor heat exchanger 20a are always operated in opposite states.
If the compressor 1a adopts a variable-capacity compressor, the variable-capacity compressor is limited by the current frequency conversion technology and the consideration of the reliability of the compressor, the lowest operation frequency of the compressor cannot be too low, generally 15% -20% of the highest operation frequency, and if the heat exchange quantity of the indoor heat exchanger 9a is positive when working in an evaporation state and negative when working in a condensation state, the continuous adjusting capacity of the conventional variable-capacity heat pump system is lost when the load is output by + 15% -15%, the system can only be controlled by starting and stopping, the fluctuation of the indoor temperature control is large, and particularly when the system works close to the zero point of the load, the temperature control can be seriously disordered.
Disclosure of Invention
The invention aims to provide a heat pump system, a control method and a control device thereof, an air conditioning device and a storage medium, so as to improve the temperature control precision of the heat pump system when the heat pump system is close to a load zero point.
A first aspect of the present invention provides a heat pump system comprising:
a compressor;
an indoor heat exchanger;
a first outdoor heat exchanger;
a second outdoor heat exchanger; and
the valve assembly is respectively connected with an air outlet and an air suction port of the compressor, a first end of the indoor heat exchanger, a first end of the first outdoor heat exchanger and a first end of the second outdoor heat exchanger, a second end of the indoor heat exchanger is connected with a second end of the first outdoor heat exchanger and a second end of the second outdoor heat exchanger through a first connecting pipeline, the valve assembly is configured to control one of the first outdoor heat exchanger and the second outdoor heat exchanger and the indoor heat exchanger to be in a first state, the other of the first outdoor heat exchanger and the second outdoor heat exchanger is in a second state, and the first state and the second state are respectively one and the other of an evaporation state and a condensation state.
In some embodiments, the valve assembly includes a first four-way valve and a second four-way valve, a first port of the first four-way valve and a first port of the second four-way valve are both connected to the exhaust port of the compressor, a second port of the first four-way valve and a second port of the second four-way valve are both connected to the first end of the indoor heat exchanger, a third port of the first four-way valve is connected to the first end of the second outdoor heat exchanger, a third port of the first four-way valve is connected to the first end of the first outdoor heat exchanger, and a fourth port of the first four-way valve and a fourth port of the second four-way valve are both connected to the suction port of the compressor.
In some embodiments, the valve assembly further comprises a first control valve disposed on the connection line between the second port of the first four-way valve and the first end of the indoor heat exchanger, and a second control valve disposed on the connection line between the second port of the second four-way valve and the first end of the indoor heat exchanger.
In some embodiments, the heat pump system further comprises a first throttle device disposed on the first connection line.
In some embodiments, the heat pump system further includes a second connection pipeline connecting the first connection pipeline and the second end of the first outdoor heat exchanger, and a third connection pipeline connecting the first connection pipeline and the second end of the second outdoor heat exchanger, wherein the second connection pipeline is provided with a second throttling device, and the third connection pipeline is provided with a third throttling device.
In some embodiments, the heat pump system further comprises a first outdoor fan and a second outdoor fan, the first outdoor fan and the first outdoor heat exchanger being located in the first air duct, and the second outdoor fan and the second outdoor heat exchanger being located in the second air duct.
In some embodiments, the heat pump system further comprises:
the first temperature sensor is used for detecting the temperature of the refrigerant flowing through the first end of the indoor heat exchanger;
the second temperature sensor is used for detecting the temperature of the refrigerant flowing through the second end of the indoor heat exchanger;
the third temperature sensor is used for detecting the temperature of the refrigerant flowing through the second end of the second outdoor heat exchanger;
the fourth temperature sensor is used for detecting the temperature of the refrigerant flowing through the first end of the second outdoor heat exchanger;
the fifth temperature sensor is used for detecting the temperature of the refrigerant flowing through the second end of the first outdoor heat exchanger;
the sixth temperature sensor is used for detecting the temperature of the refrigerant flowing through the first end of the first outdoor heat exchanger;
the exhaust temperature sensor is used for detecting the temperature of a refrigerant at an exhaust port of the compressor;
the air suction temperature sensor is used for detecting the temperature of a refrigerant at an air suction port of the compressor;
the discharge pressure sensor is used for detecting the pressure of a refrigerant at a discharge port of the compressor;
and the air suction pressure sensor is used for detecting the pressure of a refrigerant at an air suction port of the compressor.
In some embodiments, the heat pump system further includes an inter-tube heat exchanger, a first flow passage and a second flow passage are arranged in the inter-tube heat exchanger, the first flow passage and the second flow passage exchange heat with each other, the valve assembly is connected with the first end of the first outdoor heat exchanger through the first flow passage, and the valve assembly is connected with the first end of the second outdoor heat exchanger through the second flow passage.
In some embodiments, the heat pump system further comprises:
the ninth temperature sensor is used for detecting the temperature of the refrigerant flowing through the first flow channel and approaching one end of the valve assembly;
and the tenth temperature sensor is used for detecting the temperature of the refrigerant flowing through the second flow passage and approaching one end of the valve assembly.
A second aspect of the present invention provides a method for controlling a heat pump system, which is applied to control the heat pump system, and includes:
determining the operation mode of the heat pump system according to the lowest output power of the compressor and the indoor load demand; and
and controlling the valve assembly to act based on the operation mode so that the indoor heat exchanger and one of the first outdoor heat exchanger and the second outdoor heat exchanger are in a first state, and the other of the first outdoor heat exchanger and the second outdoor heat exchanger is in a second state, wherein the first state and the second state are respectively one and the other of an evaporation state and a condensation state.
In some embodiments of the present invention, the,
if the indoor load demand is greater than the lowest output power of the compressor, determining that the heat pump system is in a first cooling mode or a first heating mode; and if the indoor load demand is less than the minimum output power of the compressor, determining that the heat pump system is in a second cooling mode or a second heating mode.
In some embodiments of the present invention, the,
when the heat pump system is in a first refrigeration mode, the valve component is controlled to act so that the indoor heat exchanger is in an evaporation state, and the first outdoor heat exchanger and the second outdoor heat exchanger are both in a condensation state;
when the heat pump system is in the first heating mode, the valve assembly is controlled to act, so that the indoor heat exchanger is in a condensation state, and the first outdoor heat exchanger and the second outdoor heat exchanger are in an evaporation state.
In some embodiments of the present invention, the,
when the heat pump system is in a second refrigeration mode, the valve assembly is controlled to act so that the indoor heat exchanger is in an evaporation state, one of the first outdoor heat exchanger and the second outdoor heat exchanger is in an evaporation state so that the refrigerant output by the compressor is divided, and the other one is in a condensation state;
when the heat pump system is in the second heating mode, the valve assembly is controlled to act so that the indoor heat exchanger is in a condensation state, one of the first outdoor heat exchanger and the second outdoor heat exchanger is in the condensation state so that the refrigerant output by the compressor is divided, and the other is in an evaporation state.
A third aspect of the present invention provides a method for controlling a heat pump system, which is applied to control the heat pump system, and includes:
determining the operation mode of the heat pump system according to the lowest output power of the compressor and the indoor load demand; and
and controlling the first four-way valve, the second four-way valve, the first control valve and the second control valve to act based on the operation mode so that one of the first outdoor heat exchanger and the second outdoor heat exchanger and the indoor heat exchanger are in a first state, and the other one of the first outdoor heat exchanger and the second outdoor heat exchanger is in a second state, wherein the first state and the second state are respectively one and the other of an evaporation state and a condensation state.
In some embodiments, the operating modes include: at least one of a first cooling mode, a second cooling mode, a first heating mode, and a second heating mode.
In some embodiments, when the operation mode is a first refrigeration mode, the first port and the third port of the first four-way valve are controlled to be communicated, and the second port and the fourth port of the first four-way valve are controlled to be communicated; controlling the first port and the third port of the second four-way valve to be communicated, and controlling the second port and the fourth port to be communicated; and controlling the first control valve and the second control valve to be in a conducting state; and/or when the operation mode is a first heating mode, controlling the first port and the second port of the first four-way valve to be communicated and controlling the third port and the fourth port to be communicated; controlling the first port and the second port of the second four-way valve to be communicated, and controlling the third port and the fourth port to be communicated; and controls the first control valve and the second control valve to be in a conduction state.
In some embodiments, when the operation mode is the second cooling mode, the first control valve is controlled to be cut off, and the first port and the second port of the first four-way valve are controlled to be communicated, and the third port and the fourth port of the first four-way valve are controlled to be communicated; and controlling the first port and the third port of the second four-way valve to be communicated, the second port and the fourth port to be communicated and controlling the second control valve to be in a conduction state so as to enable the second outdoor heat exchanger to be in an evaporation state.
In some embodiments, the heat pump system further includes a first throttling device disposed on the first connection line, and the control method further includes:
and controlling the target opening degree of the first throttling device according to a functional relation of a difference value between the current indoor environment temperature and the target indoor environment control temperature and/or a functional relation of the superheat degree of the indoor heat exchanger.
In some embodiments, the heat pump system further comprises a second outdoor fan in the same duct as the second outdoor heat exchanger, and the control method further comprises:
and controlling the target rotating speed of the second outdoor fan according to the functional relation of the suction pressure or the evaporation temperature.
In some embodiments, the heat pump system further comprises a third throttling device disposed on the third connecting line, and the control method further comprises:
and controlling the target opening degree of the third throttling device according to a function relation of the superheat degree of a refrigerant branch where the second outdoor heat exchanger is located.
In some embodiments, when the operation mode is the second heating mode, the first port and the second port of the first four-way valve are controlled to be communicated, the third port and the fourth port of the first four-way valve are controlled to be communicated, and the first control valve is controlled to be in a conducting state; and controlling the second control valve to be in a cut-off state, and controlling the first port and the third port of the second four-way valve to be communicated, and controlling the second port and the fourth port of the second four-way valve to be communicated, so that the first outdoor heat exchanger is in a condensation state.
In some embodiments, the target opening degree of the first throttle device is controlled as a function of a difference between the current indoor ambient temperature and the indoor ambient target control temperature.
In some embodiments, the heat pump system further comprises a first outdoor fan in the same duct as the first outdoor heat exchanger, and the control method further comprises:
and controlling the target rotating speed of the first outdoor fan according to the functional relation of the exhaust pressure or the supercooling degree.
In some embodiments, the heat pump system further includes a second throttle device disposed on the second connection line, and the control method further includes:
and controlling the target opening degree of the second throttling device according to the function relation of the supercooling degree of the refrigerant branch where the first outdoor heat exchanger is located.
In some embodiments, when the target opening degree of the first throttle device reaches a maximum value, the first port and the second port of the second four-way valve, and the third port and the fourth port of the second four-way valve are controlled to communicate such that the first outdoor heat exchanger switches from the condensing state to the evaporating state.
In some embodiments, after switching the first outdoor heat exchanger from the condensing state to the evaporating state, the control method further comprises:
controlling the target rotating speed of the first outdoor fan according to a functional relation of suction pressure or evaporation temperature; and/or the presence of a gas in the gas,
controlling the target opening degree of the second throttling device according to a function relation of the superheat degree of a refrigerant branch where the first outdoor heat exchanger is located; and/or the presence of a gas in the gas,
and controlling the target opening degree of the third throttling device according to a function relation of the superheat degree of a refrigerant branch where the second outdoor heat exchanger is located.
In some embodiments, after switching the first outdoor heat exchanger from the condensing state to the evaporating state, the control method further comprises: and controlling the second control valve to be in a conducting state.
A fourth aspect of the present invention provides a control device of a heat pump system, including:
a memory; and a processor coupled to the memory, the processor configured to execute the control method as described above based on instructions stored in the memory.
A fifth aspect of the present invention provides an air conditioning apparatus including the heat pump system as described above, and a control device of the heat pump system as described above.
A sixth aspect of the present invention provides a computer-readable storage medium storing computer instructions for a processor to execute the control method as described above.
Based on the technical scheme provided by the invention, the heat pump system comprises a compressor, an indoor heat exchanger, a first outdoor heat exchanger, a second outdoor heat exchanger and a valve assembly, wherein the valve assembly is respectively connected with an air outlet and an air suction port of the compressor, a first end of the indoor heat exchanger, a first end of the first outdoor heat exchanger and a first end of the second outdoor heat exchanger, a second end of the indoor heat exchanger is connected with a second end of the first outdoor heat exchanger and a second end of the second outdoor heat exchanger through a first connecting pipeline, the valve assembly is configured to be capable of controlling one of the first outdoor heat exchanger and the second outdoor heat exchanger and the indoor heat exchanger to be in a first state, the other one of the first outdoor heat exchanger and the second outdoor heat exchanger is in a second state, and the first state and the second state are respectively one and the other of an evaporation state and a condensation state. When the output power of the compressor of the heat pump system reaches the lowest output power and the indoor load demand is less than the lowest output power, part of the refrigerant output by the compressor can be shunted to the outdoor heat exchanger instead of being born by the indoor heat exchanger, so that the heat pump system can still accurately control the indoor temperature when approaching the load zero point. And because the output refrigerant of the compressor can be shunted to the outdoor heat exchanger, when the indoor load demand is very low, the compressor does not need to work at ultralow frequency, and the running reliability of the compressor is improved.
Other features of the present invention and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:
FIG. 1 is a schematic diagram of a conventional heat pump system;
fig. 2 is a schematic structural diagram of a heat pump system according to an embodiment of the present invention;
fig. 3 is a flowchart illustrating a control method of the heat pump system according to an embodiment of the present invention;
fig. 4 is a schematic structural diagram of a heat pump system according to another embodiment of the present invention;
fig. 5 is a flowchart illustrating a method of controlling a heat pump system according to another embodiment of the present invention;
fig. 6 is a block diagram schematically illustrating a control device of the heat pump system according to the embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The relative arrangement of the components and steps, the numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
Spatially relative terms, such as "above … …," "above … …," "above … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously positioned and the spatially relative descriptors used herein interpreted accordingly.
As shown in fig. 2, a heat pump system according to an embodiment of the present invention includes:
a compressor 1;
an indoor heat exchanger 9;
a first outdoor heat exchanger 20;
the second outdoor heat exchanger 21;
the valve assembly 300 is connected to the discharge port a and the suction port b of the compressor 1, the first end g of the indoor heat exchanger 9, the first end 73 of the first outdoor heat exchanger 20, and the first end 74 of the second outdoor heat exchanger 21, respectively, and the second end h of the indoor heat exchanger 9 is connected to the second end 78 of the first outdoor heat exchanger 20 and the second end 77 of the second outdoor heat exchanger 21 through a first connecting line. The valve assembly 300 is configured to be able to control both one of the first and second outdoor heat exchangers 20 and 21 and the indoor heat exchanger 9 to be in a first state and the other of the first and second outdoor heat exchangers 20 and 21 to be in a second state, which are one and the other of an evaporating state and a condensing state, respectively.
The valve assembly 300 according to the embodiment of the present invention can control one of the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 and the indoor heat exchanger 9 to be in the first state, so that when the output power of the compressor 1 of the heat pump system according to the present invention reaches the minimum output power and the indoor load demand is less than the minimum output power, a part of the refrigerant output by the compressor 1 can be diverted to the heat exchanger located outdoors instead of being borne by the indoor heat exchanger 9, so that the heat pump system according to the present embodiment can still accurately control the indoor temperature when approaching the load zero point. In addition, because the output refrigerant of the compressor 1 of the embodiment can be distributed to the outdoor heat exchanger, when the indoor load demand is very low, the compressor 1 does not need to work at ultralow frequency, and the operation reliability of the compressor 1 is improved.
As shown in fig. 2, the compressor 1 of the present embodiment is located indoors to reduce the risk of theft. In other embodiments, the compressor may be located outdoors. The compressor 1 of the present embodiment is an inverter compressor.
Fig. 3 is a flowchart illustrating a control method of a heat pump system according to an embodiment of the present invention, and as shown in fig. 3, the control method includes the following steps:
step 301, determining the operation mode of the heat pump system according to the lowest output power of the compressor 1 and the indoor load demand; and
and step 302, controlling the valve assembly to act based on the operation mode so that one of the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 and the indoor heat exchanger 9 are in a first state, and the other of the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 is in a second state, wherein the first state and the second state are respectively one and the other of an evaporation state and a condensation state.
The control method determines the operation mode of the system according to the lowest output power and the indoor load requirement of the compressor 1, and controls the valve assembly to act according to the operation mode so as to enable one of the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 to be in the same state as the indoor heat exchanger 9, thereby enabling one outdoor heat exchanger and the indoor heat exchanger 9 to share the refrigerant output by the compressor 1 together, realizing the ultralow refrigeration/heating output of the whole heat pump system, and also keeping accurate temperature control precision.
Specifically, if the indoor load demand is greater than the minimum output power of the compressor 1, determining that the heat pump system is in a first cooling mode or a first heating mode; and if the indoor load demand is less than the minimum output power of the compressor, determining that the heat pump system is in a second cooling mode or a second heating mode.
If the indoor load demand is greater than the minimum output power of the compressor 1, the indoor load demand can be satisfied by increasing the frequency of the compressor 1, which is achievable by the conventional heat pump system, and it is determined that the heat pump system is in the first cooling mode or the first heating mode.
When the heat pump system is in the first cooling mode, the valve assembly 300 is controlled to act, so that the indoor heat exchanger 9 is in an evaporation state, and the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 are both in a condensation state;
when the heat pump system is in the first heating mode, the control valve assembly 300 is operated to make the indoor heat exchanger 9 in the condensing state and the first and second outdoor heat exchangers 20 and 21 in the evaporating state.
The control method of the two operation modes is basically the same as that of the conventional heat pump system, and the detailed description is omitted here. The embodiment of the present invention focuses on how to control the operation of the valve assembly 300 when the inverter compressor 1 reaches the minimum output power, so that the cooling/heating output of the indoor heat exchanger 9 of the present embodiment meets the indoor load requirement lower than the minimum output power.
If the indoor load demand is less than the minimum output power of the compressor 1, it is determined that the heat pump system is in the second cooling mode or the second heating mode.
When the heat pump system is in the second cooling mode, the valve assembly 300 is controlled to operate, so that the indoor heat exchanger 9 is in an evaporation state, one of the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 is in an evaporation state, so that the refrigerant output by the compressor 1 is divided, and the other is in a condensation state;
when the heat pump system is in the second heating mode, the control valve assembly 300 is operated to make the indoor heat exchanger 9 in a condensing state, one of the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 in a condensing state to make the refrigerant output by the compressor 1 split and the other in an evaporating state.
As shown in fig. 4, a valve assembly 300 according to another embodiment of the present invention includes a first four-way valve 2 and a second four-way valve 3, a first port D of the first four-way valve 2 and a first port D of the second four-way valve 3 are both connected to a discharge port a of a compressor 1, a second port E of the first four-way valve 2 and a second port E of the second four-way valve 3 are both connected to a first end g of an indoor heat exchanger 9, a third port C of the first four-way valve 2 is connected to a first end 74 of a second outdoor heat exchanger 21, a third port C of the second four-way valve 3 is connected to a first end 73 of a first outdoor heat exchanger 20, and a fourth port S of the first four-way valve 2 and a fourth port S of the second four-way valve 3 are both connected to a suction port b of.
The two outdoor heat exchangers of this embodiment are controlled its state by different cross valves respectively, and two outdoor heat exchanger states are independent each other, do not influence each other. The four-way valve is powered off, and a first port D is communicated with a third port C, and a second port E is communicated with a fourth port S; the four-way valve is electrified, and a first port D is communicated with a second port E, and a third port C is communicated with a fourth port S.
The valve assembly of this embodiment further includes a first control valve 4 and a second control valve 5, the first control valve 4 is disposed on a connection pipeline between the second port E of the first four-way valve 2 and the first end g of the indoor heat exchanger 9, and the second control valve 5 is disposed on a connection pipeline between the second port E of the second four-way valve 3 and the first end g of the indoor heat exchanger 9. The first control valve 4 and the second control valve 5 of the present embodiment may be solenoid valves, ball valves, or the like.
The heat pump system of the present embodiment further includes a first throttling device 13 provided on the first connection line. The first throttling device 13 is connected with the second end h of the indoor heat exchanger 9, and is used for throttling the refrigerant entering and exiting the indoor heat exchanger 9. The first throttling device 13 may be various throttling elements such as an electronic expansion valve, a thermal expansion valve, and a throttling orifice plate.
The heat pump system of the present embodiment further includes a second connection line connecting the first connection line and the second end 78 of the first outdoor heat exchanger 20 and a third connection line connecting the first connection line and the second end 77 of the second outdoor heat exchanger 21. A second throttling device 22 is arranged on the second connecting pipeline, and a third throttling device 23 is arranged on the third connecting pipeline. Similarly, the second throttling device 22 and the third throttling device 23 are connected to the second end 78 of the first outdoor heat exchanger 20 and the second end 77 of the second outdoor heat exchanger 21, respectively, and are used for throttling the refrigerant entering into and exiting from the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21, respectively. The second throttling device 22 and the third throttling device 23 may be various throttling elements such as an electronic expansion valve, a thermal expansion valve, and an orifice plate.
The heat pump system of the present embodiment further includes a first outdoor fan 24 and a second outdoor fan 25, the first outdoor fan 24 and the first outdoor heat exchanger 20 are located in the first air duct, and the second outdoor fan 25 and the second outdoor heat exchanger 21 are located in the second air duct. The first outdoor heat exchanger 20 is correspondingly provided with a first outdoor fan 24 for promoting heat exchange between the refrigerant flowing through the first outdoor heat exchanger 20 and outdoor air, so as to improve the heat exchange effect of the refrigerant at the first outdoor heat exchanger 20. The second outdoor heat exchanger 21 is correspondingly provided with a second outdoor fan 25 for promoting heat exchange between the refrigerant flowing through the second outdoor heat exchanger 21 and outdoor air, so as to improve the heat exchange effect of the refrigerant at the second outdoor heat exchanger 21. The first outdoor fan 24 and the first outdoor heat exchanger 20 may be located in the first air duct, the second outdoor fan 25 and the second outdoor heat exchanger 21 are located in the second air duct, and the first air duct and the second air duct are independently disposed.
In order to detect the temperature and/or pressure of the refrigerant at each position on the refrigerant flow path of the heat pump system, so as to realize the precise control of the heat pump system, the heat pump system of the embodiment further comprises a temperature and pressure detector.
Specifically, as shown in fig. 4, the heat pump system of the present embodiment includes:
the first temperature sensor 30 is configured to detect a temperature of the refrigerant flowing through the first end of the indoor heat exchanger 9. The first temperature sensor 30 is disposed at a first end g of the indoor heat exchanger 9.
The second temperature sensor 31 and the second temperature sensor 33 are configured to detect a temperature of the refrigerant flowing through the second end of the indoor heat exchanger 9. The second temperature sensor 33 is disposed at the second end h of the indoor heat exchanger 9.
And a third temperature sensor 32, wherein the third temperature sensor 32 is configured to detect a temperature of the refrigerant flowing through the second end of the second outdoor heat exchanger 21. The third temperature sensor 32 is disposed at the second end 77 of the second outdoor heat exchanger 21.
And a fourth temperature sensor 33, wherein the fourth temperature sensor 33 is used for detecting the temperature of the refrigerant flowing through the first end of the second outdoor heat exchanger 21. The fourth temperature sensor 33 is provided at the first end 74 of the second outdoor heat exchanger 21.
And a fifth temperature sensor 34, wherein the fifth temperature sensor 34 is used for detecting the temperature of the refrigerant flowing through the second end of the first outdoor heat exchanger 20. The fifth temperature sensor 34 is disposed at the second end 78 of the first outdoor heat exchanger 20.
And a sixth temperature sensor 35, wherein the sixth temperature sensor 35 is configured to detect a temperature of the refrigerant flowing through the first end of the first outdoor heat exchanger 20. The sixth temperature sensor is disposed at the first end 73 of the first outdoor heat exchanger 20.
The discharge temperature sensor 38, the discharge temperature sensor 38 is used for detecting the temperature of the refrigerant at the discharge port of the compressor 1. The discharge temperature sensor 38 is provided on the discharge pipe 60 of the compressor 1.
And an intake temperature sensor 39, the intake temperature sensor 39 being configured to detect a temperature of the refrigerant at the intake port of the compressor 1. The intake air temperature sensor 39 is provided on the intake pipe 61 of the compressor 1.
And the discharge pressure sensor 40, the discharge pressure sensor 40 is used for detecting the refrigerant pressure at the discharge port of the compressor 1. The discharge pressure sensor 40 is provided on the discharge pipe 60 of the compressor 1. The actual pressure measured by the exhaust pressure sensor 40 is the system high pressure HPS. The saturation thermometer corresponding to the high-pressure HPS of the system is THPS。
A suction pressure sensor 41, the suction pressure sensor 41 is used for detecting the pressure of the refrigerant at the suction port of the compressor 1. The suction pressure sensor 41 is provided in the suction pipe 61 of the compressor 1. The actual measurement by the inspiratory pressure sensor 41 is the system low pressure LPS. The saturation thermometer corresponding to the low-pressure LPS of the system is TLPS。
In some embodiments, the heat pump system further includes an inter-tube heat exchanger 12, the inter-tube heat exchanger 12 is provided with a first flow passage and a second flow passage for exchanging heat with each other, the valve assembly is connected to the first end 73 of the first outdoor heat exchanger 20 through the first flow passage, and the valve assembly is connected to the first end 74 of the second outdoor heat exchanger 21 through the second flow passage. When the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 are in different states, a temperature difference exists between the refrigerant flowing through the first flow path and the second flow path of the inter-tube heat exchanger 12, and therefore the refrigerant between the two flow paths can exchange heat in the inter-tube heat exchanger 12, so that the loads of the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 are effectively reduced, and further, the rotating speeds of the first outdoor fan 24 and the second outdoor fan 25 are effectively reduced to reduce power consumption.
In some embodiments, the heat pump system further comprises:
a ninth temperature sensor 36, wherein the ninth temperature sensor 36 is used for detecting the temperature of the refrigerant flowing through the first flow channel and approaching one end of the valve assembly;
the tenth temperature sensor 37, the tenth temperature sensor 37 is used for detecting the temperature of the refrigerant flowing through the second flow passage near one end of the valve assembly.
As shown in fig. 5, the control method of the heat pump system of the present embodiment includes the steps of:
step 501, determining an operation mode of a heat pump system according to the lowest output power of a compressor and an indoor load demand; and
and 502, controlling the first four-way valve 2, the second four-way valve 3, the first control valve 4 and the second control valve 5 to act based on the operation mode.
The operation mode of the present embodiment includes at least one of a first cooling mode, a second cooling mode, a first heating mode, and a second heating mode.
In some embodiments, when the operation mode is the first cooling mode, the first port D and the third port C of the first four-way valve 2 are controlled to be communicated, and the second port E and the fourth port S are controlled to be communicated; controlling the first port D and the third port C of the second four-way valve 3 to be communicated, and controlling the second port E and the fourth port S to be communicated; and controls the first control valve 4 and the second control valve 5 to be in a conduction state. At this time, the indoor heat exchanger 9 is in an evaporation state, and both the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 are in a condensation state.
When the operation mode is a first heating mode, controlling the first port D and the second port E of the first four-way valve 2 to be communicated, and controlling the third port C and the fourth port S to be communicated; controlling the first port D and the second port E of the second four-way valve 3 to be communicated, and controlling the third port C and the fourth port S to be communicated; and controls the first control valve 4 and the second control valve 5 to be in a conduction state. At this time, the indoor heat exchanger 9 is in a condensing state, and the first and second outdoor heat exchangers 20 and 21 are in an evaporating state.
In some embodiments, when the operation mode is the second cooling mode, the first control valve 4 is controlled to be closed and the first port D and the second port E of the first four-way valve 2 are controlled to be communicated, and the third port C and the fourth port S of the first four-way valve are controlled to be communicated; and controlling the first port D and the third port C of the second four-way valve 3 to be communicated, the second port E and the fourth port S to be communicated and controlling the second control valve 5 to be in a conduction state so as to enable the second outdoor heat exchanger to be in an evaporation state. The high-pressure refrigerant discharged from the discharge port a of the compressor 1 flows to the second four-way valve 3 through the branch 63, flows into the first outdoor heat exchanger 20 for condensation and heat release, and then flows into the second outdoor heat exchanger 21 and the indoor heat exchanger 9 for evaporation and heat absorption from the intersection point K. In the second cooling mode, the second outdoor heat exchanger 21 and the indoor heat exchanger 9 share the cooling capacity output by the compressor 1 together, so that the indoor temperature can be accurately controlled when the lowest output power of the compressor 1 is greater than the indoor load demand.
In some embodiments, the heat pump system further includes a first throttling device 13 disposed on the first connection line, and the control method further includes:
the target opening degree of the first throttle device 13 is controlled according to a functional relation of a difference between the current indoor environment temperature and the target indoor environment control temperature and/or a functional relation of a superheat degree of the indoor heat exchanger 9.
Preferably, the target opening degree of the first throttle device 13 is controlled according to a difference between the current indoor ambient temperature and the target indoor ambient control temperature on the basis of ensuring the degree of superheat of the indoor heat exchanger 9. The degree of superheat of the indoor heat exchanger 9 is represented by a refrigerant temperature difference between both ends of the indoor heat exchanger 9.
In some embodiments, the heat pump system further includes a second outdoor fan 25 in the same duct as the second outdoor heat exchanger 21, and the control method further includes:
the target rotation speed of the second outdoor fan 25 is controlled according to the functional relation of the suction pressure or the evaporation temperature.
In some embodiments, the heat pump system further comprises a third throttling device 23 arranged on the third connecting line, and the control method further comprises:
the target opening degree of the third throttling device 23 is controlled according to the function relation of the superheat degree of the refrigerant branch where the second outdoor heat exchanger 21 is located. At this time, the second outdoor heat exchanger 21 is in an evaporation state, and the opening degree of the third throttling device 23 is controlled to ensure the superheat degree of the refrigerant flow path where the second outdoor heat exchanger 21 is located.
In some embodiments, when the operation mode is the second heating mode, the first port D and the second port E of the first four-way valve 2 are controlled to communicate, the third port C and the fourth port S are controlled to communicate, and the first control valve 4 is controlled to be in a conducting state; the second control valve 5 is controlled to be in a cut-off state and the first port D and the third port C and the second port E and the fourth port S of the second four-way valve 3 are controlled to be communicated so that the first outdoor heat exchanger 20 is in a condensing state. The high-pressure refrigerant discharged from the discharge port a of the compressor 1 flows to the first four-way valve 2 through the branch 62 and flows to the indoor heat exchanger 9, and flows to the second four-way valve 3 through the branch 63 and flows to the first outdoor heat exchanger 20. In the second heating mode, the first outdoor heat exchanger 20 and the indoor heat exchanger 9 share the heating capacity output by the compressor 1 together, so that the indoor temperature can be accurately controlled even when the minimum output power of the compressor 1 is greater than the indoor load demand.
In some embodiments, the target opening degree of the first throttle device 13 is controlled as a function of a difference between the current indoor ambient temperature and the indoor ambient target control temperature.
In some embodiments, the heat pump system further includes a first outdoor fan 24 in the same duct as the first outdoor heat exchanger 20. At this time, the first outdoor heat exchanger 20 is in a condensing state, and the control method further includes:
the target rotation speed of the first outdoor fan 24 is controlled according to the functional relation of the discharge pressure or the supercooling degree.
In some embodiments, the heat pump system further comprises a second throttle 22 arranged on the second connecting line. At this time, the first outdoor heat exchanger 20 is in a condensing state, and the opening degree of the second throttling device 22 is controlled to ensure the supercooling degree of the refrigerant flow path where the first outdoor heat exchanger 20 is located.
The control method further comprises the following steps:
the target opening degree of the second throttling device 22 is controlled according to the function relation of the supercooling degree of the refrigerant branch where the first outdoor heat exchanger 20 is located.
When the target opening degree of the first throttle device 13 reaches the maximum value, the first port D and the second port E of the second four-way valve 3 are controlled to communicate, and the third port C and the fourth port S to communicate such that the first outdoor heat exchanger 20 is switched from the condensing state to the evaporating state.
In some embodiments, after switching the first outdoor heat exchanger 20 from the condensing state to the evaporating state, the control method further includes:
controlling the target rotating speed of the first outdoor fan according to a functional relation of suction pressure or evaporation temperature; and/or the presence of a gas in the gas,
controlling the target opening degree of the second throttling device 22 according to a function relation of the superheat degree of the refrigerant branch where the first outdoor heat exchanger 20 is located; and/or the presence of a gas in the gas,
the target opening degree of the third throttling device 23 is controlled according to the function relation of the superheat degree of the refrigerant branch where the second outdoor heat exchanger 21 is located.
In some embodiments, after switching the first outdoor heat exchanger 20 from the condensing state to the evaporating state, the control method further includes: the second control valve 5 is controlled to the on state. After switching the second control valve 5 to the conducting state, the heat pump system has entered the first heating mode, i.e. the normal heating mode.
A heat pump system and a control method thereof according to an embodiment of the present invention will be described in detail with reference to fig. 4 and 5.
As shown in fig. 4, the heat pump system according to the embodiment of the present invention includes an indoor unit 100 and an outdoor unit 200.
The indoor unit 100 includes a compressor 1, a first four-way valve 2, a second four-way valve 3, a first control valve 4, a second control valve 5, an indoor fan 7, an indoor heat exchanger 9, a first throttling device 13, a first cut-off valve 14, a second cut-off valve 15, a third cut-off valve 16, an exhaust temperature sensor 38, an intake temperature sensor 39, an exhaust pressure sensor 40, an intake pressure sensor 41, a first temperature sensor 30, and a second temperature sensor 31.
The exhaust port a of the compressor 1 is divided into two branches, the first branch 62 is connected to the first port D of the first four-way valve 2, and the second branch 63 is connected to the first port D of the second four-way valve 3. The suction port b of the compressor 1 is divided into two paths which are respectively connected with the fourth port S of the first four-way valve 2 and the fourth port S of the second four-way valve 3; the second port E of the first four-way valve 2 is connected to a first end 45 of the first control valve 4 and the second port E of the second four-way valve 3 is connected to a first end 46 of the second control valve 5. The second end 47 of the first control valve 4 and the second end 48 of the second control valve 5 are connected with the first end g of the indoor heat exchanger 9. A second end h of the indoor heat exchanger 9 is provided with a first connection pipe for connection with the outdoor unit 200, and the first connection pipe is provided with a first throttling device 13 and a third stop valve 16 connected in series. The discharge temperature sensor 38 and the discharge pressure sensor 40 are placed on a discharge line 60 of the compressor 1, and the suction temperature sensor 39 and the suction pressure sensor 41 are placed on a suction line 61 of the compressor 1. The first cut valve 14 is provided on a connection line of the third port C of the second four-way valve 3. The second cut-off valve 15 is provided on a connection pipe of the third port C of the first four-way valve 2.
The outdoor unit 200 includes a first outdoor heat exchanger 20, a second outdoor heat exchanger 21, a second throttling device 22, a third throttling device 23, a first outdoor fan 24, a second outdoor fan 25, the inter-tube heat exchanger 12, a third cut-off valve 17, a fourth cut-off valve 18, a fifth cut-off valve 19, a third temperature sensor 32, a fourth temperature sensor 33, a fifth temperature sensor 34, a sixth temperature sensor 35, a seventh temperature sensor 36, and an eighth temperature sensor 37.
The second end 78 of the first outdoor heat exchanger 20 is provided with a second connection pipe, and the second end 77 of the second outdoor heat exchanger 21 is provided with a third connection pipe. The second connecting pipeline and the third connecting pipeline are intersected at a point k and are connected with the first connecting pipeline through a fourth connecting pipeline. Wherein, a second throttling device 22 is arranged on the second connecting pipeline, and a third throttling device 23 is arranged on the third connecting pipeline. A fifth stop valve 19 is arranged on the fourth connecting pipeline.
At first ends of the first and second outdoor heat exchangers 20 and 21, the inter-tube heat exchanger 12 is disposed. Two flow passages, namely a first flow passage and a second flow passage, are arranged in the inter-tube heat exchanger 12, and the two flow passages are mutually separated and exchange heat with each other. The inter-tube heat exchanger 12 has four flow ports in total, which are a first flow port q, a second flow port p, a third flow port m, and a fourth flow port n, respectively. The first flow port q and the third flow port m are respectively located at two ends of the first flow channel, and the second flow port p and the fourth flow port n are respectively located at two ends of the second flow channel. The first port q is connected to a port 76 of the third stop valve 17, the second port p is connected to a port 75 of the fourth stop valve 18, the third port m is connected to the first end 73 of the first outdoor heat exchanger 20, and the fourth port n is connected to the first end 74 of the second outdoor heat exchanger 21.
The third temperature sensor 32 is placed at the second end 77 of the second outdoor heat exchanger 21. The fourth temperature sensor 33 is placed at the first end 74 of the second outdoor heat exchanger 21. The fifth temperature sensor 34 is placed at the second end 78 of the first outdoor heat exchanger 20. The sixth temperature sensor 35 is placed at the first end 73 of the first outdoor heat exchanger 20, and the seventh temperature sensor 36 is placed on the pipe on the first circulation port q side of the inter-pipe heat exchanger 12. The eighth temperature sensor 37 is placed on the pipe on the second flow port p side of the inter-pipe heat exchanger 12. The first outdoor fan 24 and the first outdoor heat exchanger 20 are in the same air duct, the second outdoor fan 25 and the second outdoor heat exchanger 21 are in the same air duct, and the two air ducts are independent and do not interfere with each other.
When the first four-way valve 2 is powered off, the first port D is communicated with the third port C, and the second port S is communicated with the fourth port E. When the power is on, the first port D is communicated with the fourth port E, and the second port S is communicated with the third port C. The second four-way valve 3 and the first four-way valve 2 are in the same state when power is on and power is off.
The first control valve 4 and the second control valve 5 of the present embodiment may be solenoid valves, ball valves, or the like. The first throttle 13, the second throttle 22 and the third throttle 23 may be electronic expansion valves or the like. The first control valve 4, the second control valve 5, the first throttling device 13, the second throttling device 22 and the third throttling device 23 of the present embodiment are all controlled by proportional pulses. The corresponding opening degree of the first control valve 4 and the second control valve 5 when the flow is maximum is defined as
Figure BDA0002785708040000201
The maximum corresponding opening degree of the first, second and third throttle devices 13, 22 and 23 is
Figure BDA0002785708040000202
When the heat pump system is in the first cooling mode, the first four-way valve 2 and the second four-way valve 3 are powered off, at this time, the indoor heat exchanger 9 works in an evaporation state, the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 both work in a condensation state, and the state is basically the same as that of the conventional heat pump system.
In the first heating mode of the heat pump system, the first four-way valve 2 and the second four-way valve 3 are powered on, and at this time, the indoor heat exchanger 9 works in a condensing state, and both the first outdoor heat exchanger 20 and the second outdoor heat exchanger 21 work in an evaporating state, which is substantially the same as that of the conventional heat pump system.
The following is a detailed description of how the heat pump system adjusts the cooling/heating output of the indoor heat exchanger to meet the cold/heat load of the indoor environment when the variable capacity compressor reaches the minimum output and the conventional heat pump system loses the continuous adjustment capability, and how the switching between the cooling mode and the heating mode is accomplished when the indoor load passes through the zero point.
STEP1：
When the indoor cooling load demand decreases, the output of the variable capacity compressor decreases and the minimum output has been reached. Assuming a minimum output of the variable capacity compressor to be
Figure BDA0002785708040000203
And the states of all components of the heat pump system after the system is stabilized are shown in table 1.
The opening degree of the first throttle device 13 is controlled at this time to make the indoor ambient temperature conform to the target control temperature on the basis of ensuring the degree of superheat of the indoor heat exchanger 9.
Specifically, as shown in the following equation, the target opening degree of the first throttle device 13 may be controlled using a functional relation of a difference between the current indoor ambient temperature and the indoor ambient target control temperature and/or a functional relation of a degree of superheat of the indoor heat exchanger 9.
Target opening degree of the first throttle device 13
Figure BDA0002785708040000204
1) When T isSensor30-TSensor31When the ratio is more than or equal to 0:
TID-Amb-TID-Tarwhen > 0, the target opening degree of the first throttle device 13
Figure BDA0002785708040000205
Increasing and conversely decreasing, TID-Amb-TID-TarWhen the opening degree is 0, the first throttle device 13 maintains the current opening degree;
2) when T isSensor30-TSensor31If < 0, the target opening degree of the first throttle device 13
Figure BDA0002785708040000211
And decreases.
STEP2：
When the indoor cooling load demand is reduced, TID-AmbDecrease, i.e. decrease of the current indoor ambient temperature, at T according to the above target opening formula of the first throttle device 13ID-AmbAfter the lowering, the opening degree of the first throttle device 13 is decreased.
Since the output of the compressor 1 is already the lowest output, but the lowest output is still larger than the required refrigeration load, part of the refrigerant output from the compressor is diverted to the first heat exchanger 21. But also to prevent the indoor heat exchanger 9 from frosting caused by the first throttle device 13 being too small in opening degree. At this time, the following steps are performed,
when T isLPSOr TSensor31Less than a certain temperature value TC1The method comprises the following steps:
1) the opening degree of the first control valve 4 is controlled by
Figure BDA0002785708040000212
Adjusting to zero;
2) the first four-way valve 2 is energized, and the second outdoor heat exchanger 21 is switched to the evaporating state.
The heat pump system of the present embodiment enters the first cooling mode through the above two steps.
STEP3：
1) Further, in order to ensure the accuracy of the indoor temperature control, the target rotation speed of the second outdoor fan 25 is controlled according to the functional relation of the suction pressure or the evaporation temperature to ensure that the suction pressure is constant and/or the evaporation temperature is constant.
Specifically, the target rotation speed of the second outdoor fan 25 is made
Figure BDA0002785708040000213
One of the following formulas (i) or a combination, calculation, etc. of variables used in formula (i) may be used:
Figure BDA0002785708040000214
taking the formula (r) as an example, when TLPS＞TC2The target rotation speed of the second outdoor fan 25
Figure BDA0002785708040000215
Increasing and conversely decreasing when T isLPS＝TC2At this time, the second outdoor fan 25 maintains the current rotation speed, TC2＞TC1。
2) Preferably, the second outdoor heat exchanger 21 is in an evaporation state, and the opening degree of the third throttling device 23 is controlled to ensure the superheat degree of the refrigerant flow path in which the second outdoor heat exchanger 21 is located. The target opening degree of the third throttling device 23 may be one of (i), (ii), (iv), or a combination, calculation, and the like of variables used in (i), (ii), (iv):
Figure BDA0002785708040000221
taking the formula (i) as an example,
Figure BDA0002785708040000222
while the third throttling means 23 is open
Figure BDA0002785708040000223
Increasing;
Figure BDA0002785708040000224
while the third throttling means 23 is open
Figure BDA0002785708040000225
The change is not changed;
Figure BDA0002785708040000226
while the third throttling means 23 is open
Figure BDA0002785708040000227
And decreases.
As can be seen from the above, when the indoor cooling load demand is reduced, the first throttling device 13, the second throttling device 23 and the second outdoor fan 25 are adjusted so that the "surplus" cooling capacity output by the compressor 1 is bypassed to the second outdoor heat exchanger 21. In this state, the second outdoor heat exchanger 21 is in an evaporation state, and the first outdoor heat exchanger 20 is in a condensation state, so that in the two flow paths of the inter-tube heat exchanger 12, the first flow path releases heat for condensation, the second flow path absorbs heat for evaporation, and the first flow path and the second flow path exchange heat with each other, thereby effectively reducing the condensation load of the first outdoor heat exchanger 20 and the evaporation load of the second outdoor heat exchanger 21, and effectively reducing the rotation speeds of the first outdoor fan 24 and the second outdoor fan 25, thereby reducing the control power consumption.
If the target opening degree of the first throttle device 13
Figure BDA0002785708040000228
When the temperature drops to zero, the output refrigerating capacity of the indoor heat exchanger 9 is zero, which indicates that the indoor cooling load demand is zero, and at this time, the system is in a complete heat recovery state.
STEP4：
If the indoor cooling load demand continues to decrease, this indicates that the indoor demand is now converted to a heat load. The heat pump system needs to enter a second heating mode, and in order to prevent the high-pressure refrigerant at the first end g of the indoor heat exchanger 9 from flowing to the second four-way valve 3 through the second control valve 5, the opening degree of the second control valve 5 is controlled by the control valve 5
Figure BDA0002785708040000231
Adjust to zero. At this time, the first outdoor heat exchanger 20 is switched to the condensation state. At this point the following steps are performed:
1) the opening degree of the first control valve 4 is adjusted from zero to
Figure BDA0002785708040000232
2)
TID-Amb-TID-TarIf < 0, the target opening degree of the first throttle device 13
Figure BDA0002785708040000233
Increasing;
TID-Amb-TID-Tarwhen 0, the target opening degree of the first throttle device 13
Figure BDA0002785708040000234
The change is not changed;
TID-Amb-TID-Tarwhen > 0, the target opening degree of the first throttle device 13
Figure BDA0002785708040000235
And decreases.
3) Preferably, the rotation speed of the first outdoor fan 24 is controlled in the second heating mode to ensure that the discharge pressure or the condensing temperature is constant.
Specifically, the target rotational speed of the first outdoor fan 24
Figure BDA0002785708040000236
The control method can be one of the control modes in the formula (i) or the combination, calculation and the like of the variables used in the formula (i):
Figure BDA0002785708040000237
taking formula (i) as an example:
THPS＞TH1the target rotational speed of the first outdoor fan 24
Figure BDA0002785708040000238
(ii) is increased;
THPS＝TH1meanwhile, the target rotational speed of the first outdoor fan 24 is kept unchanged;
THPS＜TH1the target rotational speed of the first outdoor fan 24
Figure BDA0002785708040000239
And decreases.
4) Preferably, the target opening degree of the second throttle device 22 is controlled according to a functional relation of the degree of superheat of the refrigerant branch in which the first outdoor heat exchanger 20 is located. Specifically, the second throttle device 22 is targeted to the opening degree
Figure BDA00027857080400002310
One of (i) and (ii), or a combination, calculation, etc. of variables used in formula (i) and (ii):
Figure BDA00027857080400002311
taking formula (i) as an example:
THPS-TSensor34＞TH2the target opening degree of the second throttle device 22
Figure BDA00027857080400002312
Increasing;
THPS-TSensor34＝TH2the target opening degree of the second throttle device 22
Figure BDA00027857080400002313
The change is not changed;
THPS-TSensor34＜TH2the target opening degree of the second throttle device 22
Figure BDA0002785708040000241
And decreases.
5) Preferably, the target rotation speed of the second outdoor fan 25
Figure BDA0002785708040000242
The control method can be one of the control modes in the formula (i) or the combination, calculation and the like of the variables used in the formula (i):
Figure BDA0002785708040000243
taking formula (i) as an example:
TLPS＜TH3the target rotational speed of the second outdoor fan 25
Figure BDA0002785708040000244
(ii) is increased;
TLPS＝TH1the target rotational speed of the second outdoor fan 25
Figure BDA0002785708040000245
The change is not changed;
TLPS＞TH1the target rotational speed of the second outdoor fan 25
Figure BDA0002785708040000246
And decreases.
6) Target opening degree of the third throttle device 23
Figure BDA0002785708040000247
Control is the same as "SETP 3-2".
STEP5：
T increases with the heat load in the roomID-AmbWith a downward trend, the target opening degree of the first throttle device 13
Figure BDA0002785708040000248
Will increase continuously when
Figure BDA0002785708040000249
When the maximum heating amount is reached, the heating amount output by the indoor heat exchanger 9 reaches the maximum, and at this time, the first outdoor heat exchanger 20 needs to be switched from the condensation state to the evaporation state.
1) The second four-way valve 3 is changed from power-off to power-on.
2) Target rotation speed of the first outdoor fan 24
Figure BDA00027857080400002410
Control is the same as "SETP 4-5".
3) Preferably, the target opening degree of the second throttle device 22
Figure BDA00027857080400002411
The variable combination and calculation can be one item in the formula (i) and (iv), or the variable combination and calculation used in the formula (i) and (iv):
Figure BDA00027857080400002412
taking formula (i) as an example:
Figure BDA00027857080400002413
target opening degree of the second throttle device 22
Figure BDA00027857080400002414
Increasing;
Figure BDA0002785708040000251
target opening degree of the second throttle device 22
Figure BDA0002785708040000252
The change is not changed;
Figure BDA0002785708040000253
target opening degree of the second throttle device 22
Figure BDA0002785708040000254
And decreases.
4) Preferably, the third throttling means 23 target opening degree
Figure BDA0002785708040000255
The variable combination and calculation can be one item in the formula (i) and (iv), or the variable combination and calculation used in the formula (i) and (iv):
Figure BDA0002785708040000256
taking formula (i) as an example:
Figure BDA0002785708040000257
target opening degree of the third throttling means 23
Figure BDA0002785708040000258
Increasing;
Figure BDA0002785708040000259
target opening degree of the third throttling means 23
Figure BDA00027857080400002510
The change is not changed;
Figure BDA00027857080400002511
target opening degree of the third throttling means 23
Figure BDA00027857080400002512
And decreases.
5) The opening degree of the second control valve 5 is adjusted from zero to
Figure BDA00027857080400002513
STEP6：
The target opening degree of the first throttle device 13 if the indoor heat load increases
Figure BDA00027857080400002514
Will increase continuously when
Figure BDA00027857080400002515
When the maximum value is reached again, the heating capacity output by the indoor heat exchanger 09 reaches the maximum output value of the minimum operation load of the variable capacity compressor, and then the adjustment of the system is switched to the normal heating mode, which is not described herein again.
In one embodiment, fig. 6 is a block schematic diagram of one embodiment of a control device of a heat pump system according to the present disclosure. As shown in fig. 6, the apparatus may include a memory 131, a processor 132, a communication interface 133, and a bus 134. The memory 131 is used for storing instructions, the processor 132 is coupled to the memory 131, and the processor 132 is configured to execute a control method for implementing the heat pump system in any of the above embodiments based on the instructions stored in the memory 131.
The memory 131 may be a high-speed RAM memory, a non-volatile memory (non-volatile memory), or the like, and the memory 131 may be a memory array. The storage 131 may also be partitioned, and the blocks may be combined into virtual volumes according to certain rules. The processor 132 may be a central processing unit CPU, or an application specific integrated circuit ASIC, or one or more integrated circuits configured to implement the control method of the heat pump system of the present disclosure.
In one embodiment, the present invention provides an air conditioning apparatus, including the heat pump system according to any of the above embodiments, and a control device of the heat pump system according to any of the above embodiments.
In one embodiment, the present invention provides a computer readable storage medium storing computer instructions which, when executed by a processor, implement a method of controlling a heat pump system as in any one of the above embodiments.
The method and system of the present invention may be implemented in a number of ways. For example, the methods and systems of the present invention may be implemented in software, hardware, firmware, or any combination of software, hardware, and firmware. The above-described order for the steps of the method is for illustrative purposes only, and the steps of the method of the present invention are not limited to the order specifically described above unless specifically indicated otherwise. Furthermore, in some embodiments, the present invention may also be embodied as a program recorded in a recording medium, the program including machine-readable instructions for implementing a method according to the present invention. Thus, the present invention also covers a recording medium storing a program for executing the method according to the present invention.
TABLE 1 table of meanings of various variables in examples of the present invention
Figure BDA0002785708040000261
Figure BDA0002785708040000271
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention and not to limit it; although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art will understand that: modifications to the specific embodiments of the invention or equivalent substitutions for parts of the technical features may be made; without departing from the spirit of the present invention, it is intended to cover all aspects of the invention as defined by the appended claims.

Claims (30)

1. A heat pump system, comprising:
a compressor (1);
an indoor heat exchanger (9);
a first outdoor heat exchanger (20);
a second outdoor heat exchanger (21); and
a valve assembly connected to an exhaust port and a suction port of the compressor (1), a first end of the indoor heat exchanger (9), a first end of the first outdoor heat exchanger (20), and a first end of the second outdoor heat exchanger (21), respectively, a second end of the indoor heat exchanger (9) is connected with a second end of the first outdoor heat exchanger (20) and a second end of the second outdoor heat exchanger (21) through a first connecting pipeline, the valve assembly is configured to be able to control one of the first and second outdoor heat exchangers (20, 21) and the indoor heat exchanger (9) to be in a first state, the other of the first outdoor heat exchanger (20) and the second outdoor heat exchanger (21) is in a second state, the first state and the second state are one and the other of an evaporation state and a condensation state, respectively.
2. The heat pump system according to claim 1, wherein the valve assembly comprises a first four-way valve (2) and a second four-way valve (3), a first port (D) of the first four-way valve (2) and a first port (D) of the second four-way valve (3) are both connected to the discharge port (a) of the compressor (1), a second port (E) of the first four-way valve (2) and a second port (E) of the second four-way valve (3) are both connected to the first end (g) of the indoor heat exchanger (9), a third port (C) of the first four-way valve (2) is connected to the first end (74) of the second outdoor heat exchanger (21), a third port (C) of the first four-way valve (2) is connected to the first end (73) of the first outdoor heat exchanger (20), and a fourth port (S) of the first four-way valve (2) and a fourth port (S) of the second four-way valve (3) are both connected to the pressure pump The air inlet (b) of the compressor (1) is connected.
3. The heat pump system according to claim 2, wherein the valve assembly further comprises a first control valve (4) and a second control valve (5), the first control valve (4) being arranged on a connection line between the second port (E) of the first four-way valve (2) and the first end (g) of the indoor heat exchanger (9), the second control valve (5) being arranged on a connection line between the second port (E) of the second four-way valve (3) and the first end (g) of the indoor heat exchanger (9).
4. Heat pump system according to claim 1, characterized in that it further comprises a first throttle device (13) arranged on the first connecting line.
5. Heat pump system according to claim 1, further comprising a second connection line connecting said first connection line and a second end (78) of said first outdoor heat exchanger (20), and a third connection line connecting said first connection line and a second end (77) of said second outdoor heat exchanger (21), said second connection line being provided with a second throttling device (22), said third connection line being provided with a third throttling device (23).
6. The heat pump system of claim 1, further comprising a first outdoor fan (24) and a second outdoor fan (25), the first outdoor fan (24) and the first outdoor heat exchanger (20) being located within a first air duct, the second outdoor fan (25) and the second outdoor heat exchanger (21) being located within a second air duct.
7. The heat pump system of claim 1, further comprising:
the first temperature sensor (30), the first temperature sensor (30) is used for detecting the temperature of the refrigerant flowing through the first end of the indoor heat exchanger (9);
a second temperature sensor (31), wherein the second temperature sensor (33) is used for detecting the temperature of the refrigerant flowing through the second end of the indoor heat exchanger (9);
a third temperature sensor (32), wherein the third temperature sensor (32) is used for detecting the temperature of the refrigerant flowing through the second end of the second outdoor heat exchanger (21);
a fourth temperature sensor (33), wherein the fourth temperature sensor (33) is used for detecting the temperature of the refrigerant flowing through the first end of the second outdoor heat exchanger (21);
a fifth temperature sensor (34), wherein the fifth temperature sensor (34) is used for detecting the temperature of the refrigerant flowing through the second end of the first outdoor heat exchanger (20);
a sixth temperature sensor (35), wherein the sixth temperature sensor (35) is used for detecting the temperature of the refrigerant flowing through the first end of the first outdoor heat exchanger (20);
the exhaust temperature sensor (38), the exhaust temperature sensor (38) is used for detecting the temperature of the refrigerant at the exhaust port of the compressor (1);
the air suction temperature sensor (39), the air suction temperature sensor (39) is used for detecting the temperature of a refrigerant at an air suction port of the compressor (1);
the discharge pressure sensor (40), the discharge pressure sensor (40) is used for detecting the refrigerant pressure at the discharge outlet of the compressor (1);
the air suction pressure sensor (41), the air suction pressure sensor (41) is used for detecting the refrigerant pressure at the air suction port of the compressor (1).
8. The heat pump system according to claim 1, further comprising an inter-tube heat exchanger (12), wherein the inter-tube heat exchanger (12) is internally provided with a first flow passage and a second flow passage for exchanging heat with each other, and wherein the valve assembly is connected with the first end (73) of the first outdoor heat exchanger (20) through the first flow passage and is connected with the first end (74) of the second outdoor heat exchanger (21) through the second flow passage.
9. The heat pump system of claim 8, further comprising:
a seventh temperature sensor (36), wherein the seventh temperature sensor (36) is used for detecting the temperature of the refrigerant flowing through the first flow passage and approaching one end of the valve assembly;
and the eighth temperature sensor (37), the eighth temperature sensor (37) is used for detecting the temperature of the refrigerant flowing through the second flow passage and approaching one end of the valve assembly.
10. A control method of a heat pump system, applied to control the heat pump system according to any one of claims 1 to 9, characterized by comprising:
determining the operation mode of the heat pump system according to the lowest output power of the compressor and the indoor load demand; and
controlling the valve assembly action based on the operation mode such that the indoor heat exchanger (9) and one of the first and second outdoor heat exchangers (20, 21) are both in a first state and the other of the first and second outdoor heat exchangers (20, 21) is in a second state, the first and second states being one and the other of an evaporating state and a condensing state, respectively.
11. The method of claim 10, wherein if the indoor load demand is greater than the minimum output power of the compressor, determining that the heat pump system is in a first cooling mode or a first heating mode; and if the indoor load demand is less than the lowest output power of the compressor, determining that the heat pump system is in a second cooling mode or a second heating mode.
12. The control method of a heat pump system according to claim 10,
when the heat pump system is in a first refrigeration mode, the valve assembly is controlled to act, so that the indoor heat exchanger is in an evaporation state, and the first outdoor heat exchanger and the second outdoor heat exchanger are both in a condensation state;
when the heat pump system is in a first heating mode, the valve assembly is controlled to act, so that the indoor heat exchanger is in a condensation state, and the first outdoor heat exchanger and the second outdoor heat exchanger are in an evaporation state.
13. The control method of a heat pump system according to claim 10,
when the heat pump system is in a second refrigeration mode, controlling the valve assembly to act so that the indoor heat exchanger is in an evaporation state, one of the first outdoor heat exchanger and the second outdoor heat exchanger is in the evaporation state so that the refrigerant output by the compressor is divided, and the other one is in a condensation state;
when the heat pump system is in a second heating mode, the valve assembly is controlled to act so that the indoor heat exchanger is in a condensation state, one of the first outdoor heat exchanger and the second outdoor heat exchanger is in the condensation state so that the refrigerant output by the compressor is divided, and the other is in an evaporation state.
14. A control method of a heat pump system, applied to control the heat pump system according to any one of claims 3 to 9, characterized by comprising:
determining the operation mode of the heat pump system according to the lowest output power of the compressor and the indoor load demand; and
controlling the actions of the first four-way valve (2), the second four-way valve (3), the first control valve (4) and the second control valve (5) based on the operation mode so that one of the first outdoor heat exchanger (20) and the second outdoor heat exchanger (21) and the indoor heat exchanger (9) are in a first state, and the other one of the first outdoor heat exchanger (20) and the second outdoor heat exchanger (21) is in a second state, wherein the first state and the second state are respectively one and the other of an evaporation state and a condensation state.
15. The control method of the heat pump system according to claim 14, wherein the operation mode includes: at least one of a first cooling mode, a second cooling mode, a first heating mode, and a second heating mode.
16. The control method of a heat pump system according to claim 14, wherein when the operation mode is the first cooling mode, the first port (D) and the third port (C) of the first four-way valve (2) are controlled to communicate, and the second port (E) and the fourth port (S) are controlled to communicate; controlling the first port (D) and the third port (C) of the second four-way valve (3) to be communicated, and controlling the second port (E) and the fourth port (S) to be communicated; and controlling the first control valve (4) and the second control valve (5) to be in a conducting state; and/or when the operation mode is the first heating mode, controlling the first port (D) and the second port (E) of the first four-way valve (2) to be communicated and controlling the third port (C) and the fourth port (S) to be communicated; controlling a first port (D) and a second port (E) of the second four-way valve (3) to be communicated and a third port (C) and a fourth port (S) of the second four-way valve (3) to be communicated; and controls the first control valve (4) and the second control valve (5) to be in a conducting state.
17. The control method of the heat pump system according to claim 14, wherein when the operation mode is the second cooling mode, the first control valve (4) is controlled to be turned off and the first port (D) and the second port (E) of the first four-way valve (2) are controlled to be communicated, and the third port (C) and the fourth port (S) are controlled to be communicated; and controlling a first port (D) and a third port (C) of the second four-way valve (3) to be communicated, a second port (E) and a fourth port (S) of the second four-way valve (3) to be communicated and controlling the second control valve (5) to be in a conduction state, so that the second outdoor heat exchanger is in an evaporation state.
18. The control method of a heat pump system according to claim 17, further comprising a first throttle device (13) provided on the first connecting line, the control method further comprising:
and controlling the target opening degree of the first throttling device (13) according to a functional relation of a difference value between the current indoor environment temperature and the target indoor environment control temperature and/or a functional relation of a superheat degree of the indoor heat exchanger (9).
19. The control method of the heat pump system according to claim 17, further comprising a second outdoor fan (25) in the same duct as the second outdoor heat exchanger (21), the control method further comprising:
and controlling the target rotating speed of the second outdoor fan according to a functional relation of suction pressure or evaporation temperature.
20. The control method of a heat pump system according to claim 17, wherein the heat pump system further includes a third throttling device (23) provided on a third connecting line, the control method further comprising:
and controlling the target opening degree of the third throttling device (23) according to a function relation of the superheat degree of a refrigerant branch where the second outdoor heat exchanger (21) is located.
21. The control method of the heat pump system according to claim 14, wherein when the operation mode is the second heating mode, the first port (D) and the second port (E) of the first four-way valve (2) are controlled to communicate, the third port (C) and the fourth port (S) are controlled to communicate, and the first control valve (4) is controlled to be in a conducting state; and controlling the second control valve (5) to be in a cut-off state and controlling the first port (D) and the third port (C) of the second four-way valve (3) to be communicated and the second port (E) and the fourth port (S) to be communicated so that the first outdoor heat exchanger (20) is in a condensation state.
22. The control method of the heat pump system according to claim 21, characterized in that the target opening degree of the first throttle device (13) is controlled according to a functional relationship of a difference between a current indoor ambient temperature and an indoor ambient target control temperature.
23. The control method of a heat pump system according to claim 22, wherein said heat pump system further includes a first outdoor fan (24) in the same duct as said first outdoor heat exchanger (20), said control method further comprising:
and controlling the target rotating speed of the first outdoor fan (24) according to a function relation of the exhaust pressure or the supercooling degree.
24. The control method of the heat pump system according to claim 21, wherein the heat pump system further includes a second throttle device (22) provided on a second connecting line, the control method further comprising:
and controlling the target opening degree of the second throttling device (22) according to a function relation of the supercooling degree of the refrigerant branch where the first outdoor heat exchanger (20) is located.
25. The control method of the heat pump system according to claim 22, wherein when the target opening degree of the first throttle device reaches a maximum value, the first port (D) and the second port (E) of the second four-way valve (3) are controlled to communicate, and the third port (C) and the fourth port (S) are controlled to communicate such that the first outdoor heat exchanger (20) is switched from a condensing state to an evaporating state.
26. The control method of the heat pump system according to claim 25, wherein after switching the first outdoor heat exchanger (20) from the condensing state to the evaporating state, the control method further comprises:
controlling the target rotating speed of the first outdoor fan according to a functional relation of suction pressure or evaporation temperature; and/or the presence of a gas in the gas,
controlling the target opening degree of the second throttling device (22) according to a function relation of the superheat degree of a refrigerant branch where the first outdoor heat exchanger (20) is located; and/or the presence of a gas in the gas,
and controlling the target opening degree of the third throttling device (23) according to a function relation of the superheat degree of a refrigerant branch where the second outdoor heat exchanger (21) is located.
27. The control method of the heat pump system according to claim 23, wherein after switching the first outdoor heat exchanger (20) from the condensing state to the evaporating state, the control method further comprises: and controlling the second control valve (5) to be in a conducting state.
28. A control device of a heat pump system, characterized by comprising:
a memory; and a processor coupled to the memory, the processor configured to execute the control method of any one of claims 10 to 13, or to execute the control method of any one of claims 14 to 27, based on instructions stored in the memory.
29. An air conditioning apparatus, characterized by comprising a heat pump system according to any one of claims 1 to 9, and a control device of the heat pump system according to claim 28.
30. A computer-readable storage medium, characterized in that it stores computer instructions for execution by a processor of the control method according to any one of claims 10 to 13, or of the control method according to any one of claims 14 to 27.
CN202011297020.1A 2020-11-18 2020-11-18 Heat pump system, control method and device thereof, air conditioning equipment and storage medium Pending CN112268379A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202011297020.1A CN112268379A (en) 2020-11-18 2020-11-18 Heat pump system, control method and device thereof, air conditioning equipment and storage medium

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202011297020.1A CN112268379A (en) 2020-11-18 2020-11-18 Heat pump system, control method and device thereof, air conditioning equipment and storage medium

Publications (1)

Publication Number Publication Date
CN112268379A true CN112268379A (en) 2021-01-26

Family

ID=74339487

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202011297020.1A Pending CN112268379A (en) 2020-11-18 2020-11-18 Heat pump system, control method and device thereof, air conditioning equipment and storage medium

Country Status (1)

Country Link
CN (1) CN112268379A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115031444A (en) * 2021-03-05 2022-09-09 约克广州空调冷冻设备有限公司 Heat pump system
CN115127166A (en) * 2022-08-31 2022-09-30 宁波奥克斯电气股份有限公司 Air conditioner energy-saving system, control method thereof and air conditioner

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101169290A (en) * 2006-10-27 2008-04-30 海尔集团公司 Air conditioner device possessing water heater function
CN101788206A (en) * 2009-07-03 2010-07-28 曾华文 Outdoor double heat exchanger defrosting low-temperature heating system
CN101903716A (en) * 2007-12-18 2010-12-01 Bsh博世和西门子家用器具有限公司 Method and control device for controlling a compressor
CN102042648A (en) * 2010-11-29 2011-05-04 青岛海信日立空调系统有限公司 Heat recovery type multi-connection air condition unit
JP2015222157A (en) * 2014-05-23 2015-12-10 株式会社富士通ゼネラル Air conditioning device
CN105758075A (en) * 2016-04-01 2016-07-13 珠海格力电器股份有限公司 Sectional type heating and defrosting air-conditioning system and heating and defrosting control method implemented by same
CN105987456A (en) * 2015-02-05 2016-10-05 佛山市禾才科技服务有限公司 Multi-connected air conditioning outdoor unit, multi-connected air conditioning system and small load operation control method thereof

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101169290A (en) * 2006-10-27 2008-04-30 海尔集团公司 Air conditioner device possessing water heater function
CN101903716A (en) * 2007-12-18 2010-12-01 Bsh博世和西门子家用器具有限公司 Method and control device for controlling a compressor
CN101788206A (en) * 2009-07-03 2010-07-28 曾华文 Outdoor double heat exchanger defrosting low-temperature heating system
CN102042648A (en) * 2010-11-29 2011-05-04 青岛海信日立空调系统有限公司 Heat recovery type multi-connection air condition unit
JP2015222157A (en) * 2014-05-23 2015-12-10 株式会社富士通ゼネラル Air conditioning device
CN105987456A (en) * 2015-02-05 2016-10-05 佛山市禾才科技服务有限公司 Multi-connected air conditioning outdoor unit, multi-connected air conditioning system and small load operation control method thereof
CN105758075A (en) * 2016-04-01 2016-07-13 珠海格力电器股份有限公司 Sectional type heating and defrosting air-conditioning system and heating and defrosting control method implemented by same

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115031444A (en) * 2021-03-05 2022-09-09 约克广州空调冷冻设备有限公司 Heat pump system
CN115127166A (en) * 2022-08-31 2022-09-30 宁波奥克斯电气股份有限公司 Air conditioner energy-saving system, control method thereof and air conditioner

Similar Documents

Publication Publication Date Title
US9010135B2 (en) Refrigeration apparatus with a refrigerant collection operation between a plurality of outdoor units
CN110671777B (en) Control method and device of air conditioner and air conditioner
JPWO2009011197A1 (en) Operation control method of refrigeration cycle apparatus
US11408621B2 (en) Systems and methods for controlling free cooling and integrated free cooling
CN111051793B (en) Air conditioning apparatus
CN210832604U (en) Air conditioner
CN112268379A (en) Heat pump system, control method and device thereof, air conditioning equipment and storage medium
CN107490090A (en) Air conditioner
JPWO2019053876A1 (en) Air conditioner
CN112556233A (en) Heat pump system, control method and control device thereof, air conditioning equipment and storage medium
US11828507B2 (en) Air conditioning system and control method therefor
CN209744650U (en) Fresh air-capillary network air combined adjusting system
CN216281972U (en) Air conditioning unit
JPH02223755A (en) Air conditioner
CN207471687U (en) Air-conditioning system and the air conditioner with the air-conditioning system
JP3447435B2 (en) Multi-room air conditioner
CN207674639U (en) A kind of air conditioner heat pump system of temperature control throttling
CN213514499U (en) Heat pump system and air conditioning equipment
CN116182338A (en) Machine room air conditioner, operation control method and operation control device thereof
CN213778228U (en) Heat pump system and air conditioning equipment
CN112594949B (en) Energy-saving enthalpy difference laboratory
US20220252317A1 (en) A heat pump
CN210154138U (en) Expansion valve assembly, bidirectional throttling system and air conditioner
JP7374633B2 (en) Air conditioners and air conditioning systems
CN113757936A (en) Air conditioner control system, air conditioner and control method of air conditioner

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination