WO2016155369A1 - 多联机系统 - Google Patents

多联机系统 Download PDF

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Publication number
WO2016155369A1
WO2016155369A1 PCT/CN2015/098289 CN2015098289W WO2016155369A1 WO 2016155369 A1 WO2016155369 A1 WO 2016155369A1 CN 2015098289 W CN2015098289 W CN 2015098289W WO 2016155369 A1 WO2016155369 A1 WO 2016155369A1
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WIPO (PCT)
Prior art keywords
heat exchange
expansion valve
electronic expansion
temperature
indoor
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.)
Ceased
Application number
PCT/CN2015/098289
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English (en)
French (fr)
Inventor
罗彬�
陈俊伟
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.)
Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
Original Assignee
Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
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 Midea Group Co Ltd, GD Midea Heating and Ventilating Equipment Co Ltd filed Critical Midea Group Co Ltd
Priority to EP15887319.0A priority Critical patent/EP3279575A4/en
Priority to BR112016030920A priority patent/BR112016030920A2/pt
Priority to US15/329,847 priority patent/US20180017271A1/en
Publication of WO2016155369A1 publication Critical patent/WO2016155369A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • 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
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/029—Control issues
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/13—Mass flow of refrigerants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/191—Pressures near an expansion valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger
    • 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

Definitions

  • the invention relates to the technical field of air conditioners, and in particular to a multi-line system.
  • the two-tube heat recovery multi-connection system is one of the mainstream heat recovery multi-line systems on the market.
  • the two-tube heat recovery multi-line system can realize simultaneous cooling and heating, in order to make the cooling and heating internal machine
  • the superheat control of the shunt device is the key control point, which requires the temperature sensor to collect the temperature values before and after the heat exchange component in the shunt device to calculate the superheat.
  • the direct function of the second electronic expansion valve is to provide the subcooling degree of the refrigerant required for the heating indoor unit, and generally it is necessary to calculate the superheat degree of the flow dividing device according to the temperature values before and after the self-initiating, and then press Given the target value, the second electronic expansion valve opening is adjusted to meet the superheat requirement. Then, the scope of this control method adjustment is limited and not comprehensive enough to be improved.
  • an embodiment of the present invention provides a multi-line system, including an outdoor unit device, a flow dividing device, and a plurality of indoor unit devices, wherein the flow dividing device includes a gas-liquid separator, a first heat exchange component, a first electronic expansion valve, a second heat exchange component, a second electronic expansion valve, and a third electronic expansion valve connected in parallel with the second electronic expansion valve, the flow dividing device is configured to obtain the first electronic expansion valve The refrigerant flow rate, and when the flow rate of the refrigerant passing through the first electronic expansion valve is greater than a first preset value, the flow dividing device respectively acquires an indoor heat exchanger of each of the plurality of indoor unit devices The outlet temperature and the temperature of the refrigerant flowing into the second heat exchange unit, and calculating the superheat value according to the outlet temperature of the indoor heat exchanger of each refrigeration indoor unit and the temperature of the refrigerant flowing into the second heat exchange unit And performing PI control on the second electronic expansion valve and the third electronic expansion
  • the flow dividing device acquires the flow rate of the refrigerant passing through the first electronic expansion valve, and when the flow rate of the refrigerant passing through the first electronic expansion valve is greater than the first preset value, the flow dividing device respectively acquires more The outlet temperature of the indoor heat exchanger of each of the indoor units of the indoor unit and the temperature of the refrigerant flowing into the second heat exchange unit, and according to the outlet temperature and the inflow of the indoor heat exchanger of each of the indoor units The temperature of the refrigerant of the two heat exchange components calculates the superheat value of the flow dividing device, and performs PI control on the second electronic expansion valve and the third electronic expansion valve according to the calculated superheat value.
  • the flow dividing device calculates the superheat value according to the following formula:
  • FIG. 4 is a schematic diagram of a system when a multi-line system operates in a pure cooling mode according to an embodiment of the present invention
  • FIG. 5 is a schematic diagram of a multi-line system operating in a main cooling mode, in accordance with one embodiment of the present invention.
  • the compressor 101 has an exhaust port having first to fourth valve ports, and a first valve port communicating with one of the second valve port and the third valve port, the fourth valve port and the second valve port
  • the valve port is connected to the other of the third valve port
  • the first valve port is connected to the exhaust port of the compressor 101 through the oil separator 105
  • the fourth valve port is passed through the external gas-liquid separator 104 and the air return port of the compressor 101.
  • a check valve 108A is connected in series between the second valve port and the first port 109
  • the third valve port is connected to the first end of the outdoor heat exchanger 103.
  • the gas-liquid separator 301 has an inlet, a gas outlet and a liquid outlet, the inlet is connected to the second end of the outdoor heat exchanger 103 through the high pressure shut-off valve 40, the check valve 108B, and the gas outlet is respectively connected with the four second control valves 303A, 303B, 303C, and 303D are connected; the four first control valves 302A, 302B, 302C, and 302D are connected to the first interface 109 through the low pressure shutoff valve 50, respectively.
  • the first heat exchange component 307A and the second heat exchange component 307B may be a plate heat exchanger or a casing heat exchanger.
  • the flow dividing device calculates the superheat value according to the following formula:
  • Tm3 is the temperature of the refrigerant discharged from the first heat exchange unit to the outdoor unit
  • Tm2 is the temperature of the refrigerant flowing into the second heat exchange unit
  • the multi-line system of the embodiment of the present invention can accurately obtain the superheat value of the shunt device by judging the flow rate of the refrigerant flowing through the first electronic expansion valve, and avoid the inaccuracy of the temperature value when the large flow rate and the small flow rate are obtained.
  • the inaccuracy of the superheat value prevents the superheat control from being truly reflected, thereby enabling accurate distribution of the refrigerant in the system.
  • the outdoor unit device 10 determines that the multi-line system operates in the pure heating mode, and at this time, the four indoor unit devices perform the heating operation.
  • the flow direction of the refrigerant is: the high pressure gas passes from the exhaust port of the compressor 101 through the oil separator 105 to the four-way valve 102, and then passes through the check valve 108C, the second interface 110, and the high pressure shut-off valve 40 to the gas-liquid separator 301.
  • the high pressure gas passes through the four second control valves 303A, 303B, 303C, and 303D from the gas outlet of the gas-liquid separator 301 to the corresponding four indoor heat exchangers to become a high pressure liquid, and then the four high pressure liquids pass through the corresponding sections.
  • the first heat exchange flow path of the flow element and the four first one-way valves 305A, 305B, 305C, 305D to the second heat exchange component 307B is changed into a low-pressure gas-liquid two-phase through the second electronic expansion valve 304B, and the low-pressure gas
  • the liquid two phases pass through the second heat exchange flow path of the second heat exchange component 307B and the second heat exchange flow path of the first heat exchange component 307A to return to the outdoor unit device 10, that is, the low pressure gas and liquid two phases pass through the low pressure shutoff valve 50,
  • the first interface 109 and the check valve 108D return to the outdoor heat exchanger 103, they become low pressure gas, and the low pressure gas is returned to the compressor through the four-way valve 102 and the external gas-liquid separator 104.
  • the air return port of the machine 101 is changed into a low-pressure gas-liquid two-phase through the second electronic expansion valve 304B, and the low-pressure gas
  • the liquid two phases pass through the second heat exchange flow path
  • the outdoor unit device 10 determines that the multi-line system is operating in the main heating mode, three of the four indoor unit devices perform heating operation, and one indoor unit performs cooling operation.
  • the flow of the refrigerant for heating is: the high-pressure gas passes from the exhaust port of the compressor 101 through the oil separator 105 to the four-way valve 102, and then passes through the check valve 108C, the second port 110, and the high-pressure shut-off valve 40 to the gas.
  • the liquid separator 301, the high-pressure gas from the gas outlet of the gas-liquid separator 301 passes through three second control valves 303A, 303B, and 303C to the indoor heat exchangers in the corresponding three heating indoor units, and becomes a high-pressure liquid.
  • the four indoor unit devices perform the cooling operation.
  • the flow direction of the refrigerant is: the high pressure gas passes from the exhaust port of the compressor 101 through the oil separator 105 to the four-way valve 102, and then passes through the outdoor heat exchanger 103 to become a high-pressure liquid, and the high-pressure liquid passes through the check valve 108B, the second The interface 110, the high pressure shutoff valve 40 to the gas-liquid separator 301, the high pressure liquid passes from the liquid outlet of the gas-liquid separator 301 through the first heat exchange flow path of the first heat exchange component 307A to the first electronic expansion valve 304A and the second electromagnetic The valve 308 then passes through the first heat exchange flow path of the second heat exchange assembly 307B to the four second check valves 306A, 306B, 306C, 306D, respectively, through the four second check valves 306A, 306B, 306C, 306D
  • the outdoor unit device 10 determines that the multi-line system is operating in the main cooling mode, three of the four indoor unit devices perform cooling operation, and one indoor unit performs heating operation.
  • the flow of the refrigerant for cooling is: the high pressure gas passes from the exhaust port of the compressor 101 through the oil separator 105 to the four-way valve 102, Then, after passing through the outdoor heat exchanger 103, it becomes a high-pressure gas-liquid two-phase, and the high-pressure gas-liquid two-phase passes through the check valve 108B, the second interface 110, and the high-pressure shut-off valve 40 to the gas-liquid separator 301 for gas-liquid separation, wherein the high pressure
  • the liquid passes from the liquid outlet of the gas-liquid separator 301 through the first heat exchange passage of the first heat exchange unit 307A to the first electronic expansion valve 304A and the second solenoid valve 308, and then passes through the first exchange of the second heat exchange unit 307B.
  • the heat flow path is respectively connected to the three second check valves 306A, 306B, and 306C, and the three high-pressure liquids passing through the three second check valves 306A, 306B, and 306C respectively correspond to the throttling elements in the three indoor unit devices. It becomes a three-way low-pressure gas-liquid two-phase, and the three-way low-pressure gas-liquid two phases pass through the corresponding indoor heat exchangers and become three-way low-pressure gas, and then return to the outdoor through three first control valves 302A, 302B, and 302C.
  • the machine device 10 that is, the low pressure gas, returns to the return port of the compressor 101 through the low pressure shutoff valve 50, the first port 109, the check valve 108A, and the outer machine gas-liquid separator 104.
  • the flow of the refrigerant for heating is: the high-pressure gas that has been subjected to gas-liquid separation by the gas-liquid separator 301 passes from the gas outlet of the gas-liquid separator 301 through the second control valve 303D to the indoor heat exchanger 241 in the indoor unit device 24, The high pressure liquid is passed through the throttle element 242 in the indoor unit device 24 and then merges with the high pressure liquid passing through the first heat exchange passage of the second heat exchange unit 307B through the first check valve 305D.
  • each indoor unit device in order to realize automatic control of the pressure difference ⁇ P before and after the first electronic expansion valve 304A, each indoor unit device needs to transmit the operating parameters of the indoor unit device to the flow dividing device 30, wherein each indoor unit device
  • the operating parameters include: the operating mode of the indoor unit (such as the cooling mode, the heating mode, etc.), the degree of superheat when the indoor unit is used as the internal cooling unit, and the opening of the throttle unit when the indoor unit is used as the internal cooling unit, indoor The degree of subcooling when the machine is used as a heating internal machine, and the opening degree of the throttle device when the indoor unit is used as a heating internal machine.
  • the outdoor unit device and the flow dividing device can communicate directly, and each indoor unit device communicates with the outdoor unit device through the flow dividing device.
  • Each of the indoor unit devices is assigned an address to facilitate communication between the indoor unit devices and communication between the indoor unit devices and the flow dividing device.
  • the first indoor unit is assigned a first address
  • the second indoor unit is The device is assigned a second address, ...
  • the seventh indoor unit is assigned a seventh address.
  • each indoor unit also includes a line controller, and each indoor unit also communicates with a respective line controller.
  • the outdoor unit control unit in the outdoor unit device communicates with the control module in the flow dividing device, and the control module in the branching device communicates with the indoor unit control unit in each indoor unit device.
  • the outdoor unit control unit in the outdoor unit device acquires temperature information of the outdoor unit (such as the ambient temperature, exhaust temperature, return air temperature, heat exchange temperature, etc.) of the outdoor unit, and pressure information (such as exhaust pressure) in real time. , the return air pressure, etc.) and the operating mode of each indoor unit sent by the plurality of indoor unit devices, etc.
  • outdoor unit control unit in the device also controls the operation of components such as the compressor and the outdoor fan according to the internal logic output command signal.
  • the outdoor unit control unit in the outdoor unit device acquires the ambient temperature information, the pressure information, and the operation mode of each indoor unit device to determine the operation mode of the multi-line system, for example, When each indoor unit is running in the cooling mode, the multi-line system operation mode is the pure cooling mode; when each indoor unit is running in the heating mode, the multi-line system operation mode is the pure heating mode; when multiple indoors In the machine device, when the operation mode is the cooling mode or the heating mode, the multi-line system operation mode is the simultaneous cooling and heating mode, and the outdoor unit device transmits the corresponding mode command to the flow dividing device according to the determined system operation mode.
  • the outdoor unit controls the operation of components such as the compressor and the outdoor fan based on the internal logic output command signal.
  • the flow dividing device controls the respective state parameters according to the mode command given by the outdoor unit device.
  • the refrigerating internal machine controls the throttling element (ie, the electronic expansion valve) corresponding to itself according to its own superheat degree, and the heating internal machine is subcooled by itself.
  • the degree is controlled by its own corresponding throttling element (ie electronic expansion valve) PID and the relevant parameters are transmitted to the shunting device.
  • the refrigerating internal machine transmits the temperature value detected by the own temperature sensor, for example, the outlet temperature of the indoor heat exchanger of the refrigerating internal machine to the diverting device, and the shunting device takes an average value according to the outlet temperature of the indoor heat exchanger that operates the refrigerating internal machine. That is T2b average.
  • the flow dividing device calculates the superheat value of the flow dividing device according to different conditions:
  • the temperature of the refrigerant controls the opening degrees of the second electronic expansion valve and the third electronic expansion valve to reach the target superheat degree based on the calculated superheat value.
  • the superheat control technology can truly reflect the superheat of the system, and avoid the improper control of the superheat to affect the cooling effect of the indoor unit.
  • the multi-line system of the embodiment of the present invention accurately obtains the superheat value of the flow dividing device by judging the flow rate of the refrigerant flowing through the first electronic expansion valve, and avoids the inaccuracy of the temperature value when the large flow rate and the small flow rate are obtained.
  • the inaccuracy of the heat value prevents the superheat control from being realized, so that the accurate distribution of the refrigerant in the system can be realized, and the multi-line system has the best effect of simultaneously heating and cooling.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features either explicitly or implicitly.
  • the meaning of "a plurality” is two or more unless specifically and specifically defined otherwise.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

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Abstract

一种多联机系统，包括室外机装置（10）、分流装置（30）、多个室内机装置（21,22,23,24），其中，分流装置（30）包括气液分离器（301）、第一换热组件（307A）、第一电子膨胀阀（304A）、第二换热组件（307B）、第二电子膨胀阀（304B）、与第二电子膨胀阀（304B）并联连接的第三电子膨胀阀（304C），分流装置（30）用于获取经过第一电子膨胀阀（304A）的冷媒流量，并在经过第一电子膨胀阀（304A）的冷媒流量大于第一预设值时，分别获取每个制冷室内机装置（21,22,23,24）的室内换热器（211,221,231,241）的出口温度和流入第二换热组件（307B）的冷媒的温度以计算过热度值，以及根据过热度值对第二电子膨胀阀（304B）和第三电子膨胀阀（304C）进行PI控制。该多联机系统能够准确地计算得到分流装置的过热度，实现对系统中的冷媒准确分配，达到多联机系统同时制热制冷效果最佳的目的。

Description

多联机系统 技术领域
本发明涉及空调技术领域，特别涉及一种多联机系统。
背景技术
随着空调技术的不断发展以及人们环保意识的加强，热回收多联机系统越来越受到市场的欢迎。而两管式热回收多联机系统是目前市场上主流热回收多联机系统中的一种，其中，两管式热回收多联机系统能够实现同时制冷制热，为了使制冷制热内机都能达到较好的效果，分流装置的过热度控制是关键控制点，这就需要温度传感器采集分流装置中换热组件前后的温度值以计算过热度。
相关技术中，主制冷模式下，第二电子膨胀阀的直接作用是提供制热室内机需求冷媒的过冷度，而通常需要根据其自身前后的温度值来计算分流装置的过热度，然后按给定目标值，调节第二电子膨胀阀开度来满足过热度的要求。然后，这种控制方法调节的范围有限，也不够全面，需要进行改进。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本发明的目的在于提出一种多联机系统，能够准确地计算得到分流装置的过热度，实现对系统中的冷媒准确分配，达到多联机系统同时制热制冷效果最佳的目的。
为达到上述目的，本发明的实施例提出了一种多联机系统，包括室外机装置、分流装置、多个室内机装置，其中，所述分流装置包括气液分离器、第一换热组件、第一电子膨胀阀、第二换热组件、第二电子膨胀阀、与所述第二电子膨胀阀并联连接的第三电子膨胀阀，所述分流装置用于获取经过所述第一电子膨胀阀的冷媒流量，并在经过所述第一电子膨胀阀的冷媒流量大于第一预设值时，所述分流装置分别获取所述多个室内机装置中每个制冷室内机装置的室内换热器的出口温度和流入所述第二换热组件的冷媒的温度，并根据每个制冷室内机装置的室内换热器的出口温度和流入所述第二换热组件的冷媒的温度计算过热度值，以及根据所述过热度值对所述第二电子膨胀阀和所述第三电子膨胀阀进行PI控制。
根据本发明实施例的多联机系统，首先分流装置获取经过第一电子膨胀阀的冷媒流量，并在经过第一电子膨胀阀的冷媒流量大于第一预设值时，分流装置分别获取多 个室内机装置中每个制冷室内机装置的室内换热器的出口温度和流入第二换热组件的冷媒的温度，并根据每个制冷室内机装置的室内换热器的出口温度和流入第二换热组件的冷媒的温度计算分流装置的过热度值，以及根据该计算得到的过热度值对第二电子膨胀阀和第三电子膨胀阀进行PI控制。因此，本发明实施例的多联机系统通过判断流过第一电子膨胀阀的冷媒流量来准确获取分流装置的过热度值，避免大流量、小流量时温度取值的不准确而导致获取的过热度值的不准确，防止不能真实体现过热度控制，从而能够实现系统中冷媒的准确分配，达到多联机系统同时制热制冷效果最佳的目的。
根据本发明的一个实施例，当经过所述第一电子膨胀阀的冷媒流量小于第二预设值时，所述分流装置还获取从所述第一换热组件中排出到所述室外机装置的冷媒的温度，并根据流入所述第二换热组件的冷媒的温度和从所述第一换热组件中排出到所述室外机装置的冷媒的温度计算所述过热度值，其中，所述第二预设值小于所述第一预设值。
根据本发明的一个实施例，所述分流装置根据以下公式计算所述过热度值：
ΔSH＝T2b平均-Tm2
其中，T2b平均为每个制冷室内机装置的室内换热器的出口温度的平均值，Tm2为流入所述第二换热组件的冷媒的温度。
根据本发明的另一个实施例，所述分流装置根据以下公式计算所述过热度值：
ΔSH＝Tm3-Tm2
其中，Tm3为从所述第一换热组件中排出到所述室外机装置的冷媒的温度，Tm2为流入所述第二换热组件的冷媒的温度。
在本发明的实施例中，所述多联机系统工作在主制冷模式。
根据本发明的一个实施例，通过设置在每个制冷室内机装置的室内换热器的出口的温度传感器以检测每个制冷室内机装置的室内换热器的出口温度，并通过设置在所述第二电子膨胀阀的出口的温度传感器以检测流入所述第二换热组件的冷媒的温度。
附图说明
图1为根据本发明一个实施例的多联机系统的系统示意图；
图2为根据本发明一个实施例的多联机系统运行于纯制热模式时的系统示意图；
图3为根据本发明一个实施例的多联机系统运行于主制热模式时的系统示意图；
图4为根据本发明一个实施例的多联机系统运行于纯制冷模式时的系统示意图；
图5为根据本发明一个实施例的多联机系统运行于主制冷模式时的示意图；以及
图6为根据本发明一个实施例的多联机系统的通讯网络图。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，仅用于解释本发明，而不能解释为对本发明的限制。
下面参照附图来描述根据本发明实施例提出的多联机系统。
如图1至图5所示，本发明实施例的多联机系统包括：室外机装置10，多个室内机装置例如四个室内机装置21、22、23、24，以及分流装置30。
其中，室外机装置10包括压缩机101、四通阀102、室外换热器103、外机气液分离器104、油分离器105、第一电磁阀106、毛细管107、四个单向阀108A、108B、108C、108D，以及第一接口109和第二接口110。压缩机101具有排气口和回气口，四通阀102具有第一至第四阀口，第一阀口与第二阀口和第三阀口中的其中一个连通，第四阀口与第二阀口和第三阀口中的另一个连通，第一阀口通过油分离器105与压缩机101的排气口相连，第四阀口通过外机气液分离器104与压缩机101的回气口相连，第二阀口与第一接口109之间串联有单向阀108A，第三阀口与室外换热器103的第一端相连。
分流装置30包括气液分离器301，多个第一控制阀例如四个第一控制阀302A、302B、302C、302D，多个第二控制阀例如四个第二控制阀303A、303B、303C、303D，第一电子膨胀阀304A，第二电子膨胀阀304B，与第二电子膨胀阀304B并联连接的第三电子膨胀阀304C，四个第一单向阀305A、305B、305C、305D，四个第二单向阀306A、306B、306C、306D，第一换热组件307A和第二换热组件307B。其中，气液分离器301具有入口、气体出口和液体出口，入口通过高压截止阀40、单向阀108B与室外换热器103的第二端相连接，气体出口分别与四个第二控制阀303A、303B、303C、303D相连；四个第一控制阀302A、302B、302C、302D分别通过低压截止阀50与第一接口109相连。第一换热组件307A和第二换热组件307B可以是板式换热器，也可以是套管换热器。
如图1至图5所示，单向阀108A的第一端通过单向阀108C连接至单向阀108B和第二接口110之间，单向阀108A的第二端通过单向阀108D连接至单向阀108B和室外换热器103之间。
第一换热组件307A和第二换热组件307B分别具有第一换热流路和第二换热流路，气液分流器301的液体出口与第一换热组件307A的第一换热流路相连，第一换热组件307A的第一换热流路与第一电子膨胀阀304A相连，第一换热组件307A的第二换热流路分别与第二换热组件307B的第二换热流路和四个第一控制阀302A、302B、302C、302D相连。
如图1至图5所示，每个室内机装置均包括室内换热器和节流元件，其中，室内机装置21包括室内换热器211和节流元件212，室内机装置22包括室内换热器221和节流元件222，室内机装置23包括室内换热器231和节流元件232，室内机装置24包括室内换热器241和节流元件242。每个室内机装置中的室内换热器的第一端与对应的节流元件相连，每个室内机装置中的室内换热器的第二端与对应的第一控制阀和第二控制阀相连，每个室内机装置中的节流元件与对应的第一单向阀和第二单向阀相连，第一单向阀和第二单向阀的流向相反。并且，四个第一单向阀305A、305B、305C、305D均连接至第一公共流路，四个第二单向阀306A、306B、306C、306D均连接至第二公共流路，第二换热组件307B的第一换热流路分别与第一公共流路和第二公共流路连通，第一电子膨胀阀304A连接至第一公共流路，第二电子膨胀阀304B分别与第二换热组件307B的第二换热流路和第二公共流路相连，第一电子膨胀阀304A还并联有第二电磁阀308。
在本发明的实施例中，分流装置30用于获取经过第一电子膨胀阀304A的冷媒流量，并在经过第一电子膨胀阀304A的冷媒流量大于第一预设值时即大流量时，分流装置30分别获取所述多个室内机装置中每个制冷室内机装置的室内换热器的出口温度和流入所述第二换热组件的冷媒的温度，并根据每个制冷室内机装置的室内换热器的出口温度和流入所述第二换热组件的冷媒的温度计算过热度值，以及根据所述过热度值对所述第二电子膨胀阀和所述第三电子膨胀阀进行PI控制。
根据本发明的一个实施例，当经过所述第一电子膨胀阀的冷媒流量小于第二预设值时即小流量时，所述分流装置还获取从所述第一换热组件中排出到所述室外机装置的冷媒的温度，并根据流入所述第二换热组件的冷媒的温度和从所述第一换热组件中排出到所述室外机装置的冷媒的温度计算所述过热度值，其中，所述第二预设值小于所述第一预设值。
其中，在计算大流量时的过热度值时，所述分流装置根据以下公式计算所述过热度值：
ΔSH＝T2b平均-Tm2
其中，T2b平均为每个制冷室内机装置的室内换热器的出口温度的平均值，Tm2为流入所述第二换热组件的冷媒的温度。
在计算小流量时的过热度值时，所述分流装置根据以下公式计算所述过热度值：
ΔSH＝Tm3-Tm2
其中，Tm3为从所述第一换热组件中排出到所述室外机装置的冷媒的温度，Tm2为流入所述第二换热组件的冷媒的温度。
因此，本发明实施例的多联机系统能够通过判断流过第一电子膨胀阀的冷媒流量来准确获取分流装置的过热度值，避免大流量、小流量时温度取值的不准确而导致获取的过热度值的不准确，防止不能真实体现过热度控制，从而能够实现系统中冷媒的准确分配。
根据本发明的一个实施例，如图1至图5所示，还在并联的第一电子膨胀阀304A和第二电磁阀308的两端分别设置压力传感器309A和压力传感器309B，并且在第二换热组件307B的第一换热流路的两端还分别设置温度传感器310A和温度传感器310B。此外，还在第一换热组件307A的第二换热流路的一端设置压力传感器309C。
并且，通过设置在每个制冷室内机装置的室内换热器的出口的温度传感器以检测每个制冷室内机装置的室内换热器的出口温度，并通过设置在所述第二电子膨胀阀的出口的温度传感器以检测流入所述第二换热组件的冷媒的温度。
在本发明的实施例中，多联机系统工作在主制冷模式时进行过热度控制的。其中，需要说明的是，多联机系统的运行模式还包括纯制冷模式和纯制热模式、主制热模式。
下面就参照图2至图5来分别描述多联机系统工作在纯制热模式、主制热模式、纯制冷模式和主制冷模式时的冷媒流向。
如图2所示，室外机装置10判断多联机系统工作在纯制热模式时，此时四个室内机装置进行制热工作。其中，冷媒流向为：高压气体从压缩机101的排气口经油分离器105到四通阀102，然后经过单向阀108C、第二接口110、高压截止阀40到气液分离器301，高压气体从气液分离器301的气体出口分别经过四个第二控制阀303A、303B、303C、303D到对应的四个室内换热器，变成高压液体，然后四路高压液体经过对应的节流元件和四个第一单向阀305A、305B、305C、305D到第二换热组件307B的第一换热流路，经过第第二电子膨胀阀304B变成低压气液两相，低压气液两相经过第二换热组件307B的第二换热流路和第一换热组件307A的第二换热流路回到室外机装置10，即低压气液两相通过低压截止阀50、第一接口109、单向阀108D回到室外换热器103后变成低压气体，低压气体通过四通阀102、外机气液分离器104回到压缩 机101的回气口。
如图3所示，室外机装置10判断多联机系统工作在主制热模式时，此时四个室内机装置中有三个室内机装置进行制热工作，一个室内机装置进行制冷工作。其中，用于制热的冷媒流向为：高压气体从压缩机101的排气口经油分离器105到四通阀102，然后经过单向阀108C、第二接口110、高压截止阀40到气液分离器301，高压气体从气液分离器301的气体出口分别经过三个第二控制阀303A、303B、303C到对应的三个制热室内机装置中的室内换热器，变成高压液体，然后三路高压液体经过对应的节流元件和三个第一单向阀305A、305B、305C到第二换热组件307B的第一换热流路，经过第第二电子膨胀阀304B变成低压气液两相，低压气液两相经过第二换热组件307B的第二换热流路和第一换热组件307A的第二换热流路回到室外机装置10，即低压气液两相通过低压截止阀50、第一接口109、单向阀108D回到室外换热器103后变成低压气体，低压气体通过四通阀102、外机气液分离器104回到压缩机101的回气口。用于制冷的冷媒流向为：经过第二换热组件307B的第一换热流路的高压液体的一部分还通过第二单向阀306D流向室内机装置24中的节流元件242，变成低压气液两相，再经过室内机装置24中的室内换热器241后变成低压气体，该低压气体经过第一控制阀302D后与经过第二换热组件307B的第二换热流路和第一换热组件307A的第二换热流路的低压气液两相混合后，回到室外机装置10。
如图4所示，室外机装置10判断多联机系统工作在纯制冷模式时，此时四个室内机装置进行制冷工作。其中，冷媒流向为：高压气体从压缩机101的排气口经油分离器105到四通阀102，然后经过室外换热器103后变成高压液体，高压液体经过单向阀108B、第二接口110、高压截止阀40到气液分离器301，高压液体从气液分离器301的液体出口经过第一换热组件307A的第一换热流路到第一电子膨胀阀304A和第二电磁阀308，然后经过第二换热组件307B的第一换热流路分别到四个第二单向阀306A、306B、306C、306D，经过四个第二单向阀306A、306B、306C、306D的四路高压液体分别对应经过四个室内机装置中的节流元件后变成四路低压气液两相，四路低压气液两相分别经过对应的室内换热器后变成四路低压气体，然后对应经过四个第一控制阀302A、302B、302C、302D回到室外机装置10，即低压气体通过低压截止阀50、第一接口109、单向阀108A、外机气液分离器104回到压缩机101的回气口。
如图5所示，室外机装置10判断多联机系统工作在主制冷模式时，此时四个室内机装置中有三个室内机装置进行制冷工作，一个室内机装置进行制热工作。其中，用于制冷的冷媒流向为：高压气体从压缩机101的排气口经油分离器105到四通阀102， 然后经过室外换热器103后变成高压气液两相，高压气液两相经过单向阀108B、第二接口110、高压截止阀40到气液分离器301进行气液分离，其中，高压液体从气液分离器301的液体出口经过第一换热组件307A的第一换热流路到第一电子膨胀阀304A和第二电磁阀308，然后经过第二换热组件307B的第一换热流路分别到三个第二单向阀306A、306B、306C，经过三个第二单向阀306A、306B、306C的三路高压液体分别对应经过三个室内机装置中的节流元件后变成三路低压气液两相，三路低压气液两相分别经过对应的室内换热器后变成三路低压气体，然后对应经过三个第一控制阀302A、302B、302C回到室外机装置10，即低压气体通过低压截止阀50、第一接口109、单向阀108A、外机气液分离器104回到压缩机101的回气口。用于制热的冷媒流向为：经过气液分离器301进行气液分离的高压气体从气液分离器301的气体出口经第二控制阀303D到室内机装置24中的室内换热器241，变成高压液体，高压液体经过室内机装置24中的节流元件242后通过第一单向阀305D与经过第二换热组件307B的第一换热流路的高压液体汇合。
在本发明的实施例中，为了实现自动控制第一电子膨胀阀304A前后的压差ΔP，每个室内机装置均需要向分流装置30发送室内机装置的运行参数，其中，每个室内机装置的运行参数包括：室内机装置的运行模式(如制冷模式、制热模式等)、室内机装置作为制冷内机时的过热度、室内机装置作为制冷内机时的节流元件开度、室内机装置作为制热内机时的过冷度、室内机装置作为制热内机时的节流元件开度等。
根据本发明的一个实施例，如图6所示，室外机装置与分流装置之间可直接进行通讯，每个室内机装置通过分流装置与室外机装置进行通讯。其中，每个室内机装置分配有一个地址，便于各个室内机装置之间的通讯以及各个室内机装置与分流装置之间的通讯，例如第一室内机装置分配有第一地址，第二室内机装置分配有第二地址，…，第七室内机装置分配有第七地址。另外，每个室内机装置还包括线控器，每个室内机装置还与各自的线控器进行通讯。
进一步地，根据本发明的一个具体示例，室外机装置中的室外机控制单元与分流装置中的控制模块进行通讯，同时分流装置中的控制模块与各个室内机装置中的室内机控制单元进行通讯。其中，室外机装置中的室外机控制单元实时获取室外机装置的温度信息(如室外机装置所处环境温度、排气温度、回气温度、热交换温度等)、压力信息(如排气压力、回气压力等)以及多个室内机装置发送的每个室内机装置的运行模式等来判定多联机系统的运行模式(例如纯制热模式、主制热模式、纯制冷模式和主制冷模式)，并将多联机系统的运行模式的指令发送给分流装置。同时，室外机 装置中的室外机控制单元还根据内部逻辑输出指令信号控制压缩机和室外风机等部件运行。
具体地，当多联机系统启动后，室外机装置中的室外机控制单元获取室外机装置的环境温度信息、压力信息以及各个室内机装置的运行模式，来判断多联机系统的运行模式，例如，当各个室内机装置均运行于制冷模式时，多联机系统运行模式为纯制冷模式；当各个室内机装置均运行于制热模式时，多联机系统运行模式为纯制热模式；当多个室内机装置中，既有运行于制冷模式也有运行于制热模式时，多联机系统运行模式为同时制冷制热模式，室外机装置根据判断的系统运行模式发送相应模式指令给分流装置。同时，室外机装置根据内部逻辑输出指令信号控制压缩机和室外风机等部件运行。分流装置根据室外机装置给定的模式指令进行各个状态参数的控制。
在本发明的实施例中，首先，多个室内机装置中，制冷内机按自身过热度对其本身对应的节流元件(即电子膨胀阀)单独PID控制，制热内机按自身过冷度对其本身对应的节流元件(即电子膨胀阀)单独PID控制，并把相关参数传递给分流装置。然后，制冷内机把自己温度传感器检测到的温度值例如制冷内机的室内换热器的出口温度传递给分流装置，分流装置再根据运行制冷内机的室内换热器的出口温度取平均值即T2b平均。然后，分流装置跟据不同情况计算分流装置的过热度值：
当经过第一电子膨胀阀的冷媒流量小于第二预设值即小流量时(制冷需求小)，第一换热组件的换热量小，从第一换热组件中排出到室外机装置的冷媒的温度接近流入第二换热组件的冷媒的温度，分流装置的过热度值＝从所述第一换热组件中排出到室外机装置的冷媒的温度-流入第二换热组件的冷媒的温度。
当经过第一电子膨胀阀的冷媒流量大于第一预设值即大流量时(制冷需求大)，第一换热组件的换热量大，从第一换热组件中排出到室外机装置的冷媒的温度远大于流入第二换热组件的冷媒的温度；这时，如果采用小流量时计算方式来计算分流装置的过热度值，以调节第二电子膨胀阀和第三电子膨胀阀的开度，不能反应分流装置的真实过热度，两个电子膨胀阀越开越大，导致很多液态冷媒旁通，影响制冷内机的制冷效果。而这时分流装置可以根据运行制冷内机传递过来的制冷内机的室内换热器的出口温度来计算平均温度即T2b平均，分流装置的过热度值＝T2b平均-流入第二换热组件的冷媒的温度，根据计算到的过热度值来控制第二电子膨胀阀和第三电子膨胀阀的开度以使其达到目标过热度。此时的过热度控制技术能真实反映系统过热度，避免过热度控制不当影响室内机的制冷效果。
根据本发明实施例的多联机系统，首先分流装置获取经过第一电子膨胀阀的冷媒流量，并在经过第一电子膨胀阀的冷媒流量大于第一预设值时，分流装置分别获取多个室内机装置中每个制冷室内机装置的室内换热器的出口温度和流入第二换热组件的冷媒的温度，并根据每个制冷室内机装置的室内换热器的出口温度和流入第二换热组件的冷媒的温度计算分流装置的过热度值，以及根据该计算得到的过热度值对第二电子膨胀阀和第三电子膨胀阀进行PI控制。因此，本发明实施例的多联机系统通过判断流过第一电子膨胀阀的冷媒流量来准确获取分流装置的过热度值，避免大流量、小流量时温度取值的不准确而导致获取的过热度值的不准确，防止不能真实体现过热度控制，从而能够实现系统中冷媒的准确分配，达到多联机系统同时制热制冷效果最佳的目的。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本发明的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示 例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本发明的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本发明的限制，本领域的普通技术人员在本发明的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (6)

  1. 一种多联机系统，其特征在于，包括室外机装置、分流装置、多个室内机装置，其中，
    所述分流装置包括气液分离器、第一换热组件、第一电子膨胀阀、第二换热组件、第二电子膨胀阀、与所述第二电子膨胀阀并联连接的第三电子膨胀阀，所述分流装置用于获取经过所述第一电子膨胀阀的冷媒流量，并在经过所述第一电子膨胀阀的冷媒流量大于第一预设值时，所述分流装置分别获取所述多个室内机装置中每个制冷室内机装置的室内换热器的出口温度和流入所述第二换热组件的冷媒的温度，并根据每个制冷室内机装置的室内换热器的出口温度和流入所述第二换热组件的冷媒的温度计算过热度值，以及根据所述过热度值对所述第二电子膨胀阀和所述第三电子膨胀阀进行PI控制。
  2. 如权利要求1所述的多联机系统，其特征在于，当经过所述第一电子膨胀阀的冷媒流量小于第二预设值时，所述分流装置还获取从所述第一换热组件中排出到所述室外机装置的冷媒的温度，并根据流入所述第二换热组件的冷媒的温度和从所述第一换热组件中排出到所述室外机装置的冷媒的温度计算所述过热度值，其中，所述第二预设值小于所述第一预设值。
  3. 如权利要求1所述的多联机系统，其特征在于，所述分流装置根据以下公式计算所述过热度值：
    ΔSH＝T2b平均-Tm2
    其中，T2b平均为每个制冷室内机装置的室内换热器的出口温度的平均值，Tm2为流入所述第二换热组件的冷媒的温度。
  4. 如权利要求2所述的多联机系统，其特征在于，所述分流装置根据以下公式计算所述过热度值：
    ΔSH＝Tm3-Tm2
    其中，Tm3为从所述第一换热组件中排出到所述室外机装置的冷媒的温度，Tm2为流入所述第二换热组件的冷媒的温度。
  5. 如权利要求1-4中任一项所述的多联机系统，其特征在于，所述多联机系统工作在主制冷模式。
  6. 如权利要求1所述的多联机系统，其特征在于，通过设置在每个制冷室内机装置的室内换热器的出口的温度传感器以检测每个制冷室内机装置的室内换热器的出口 温度，并通过设置在所述第二电子膨胀阀的出口的温度传感器以检测流入所述第二换热组件的冷媒的温度。
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