WO2022257993A1 - Système de pompe à chaleur et procédé de commande associé - Google Patents

Système de pompe à chaleur et procédé de commande associé Download PDF

Info

Publication number
WO2022257993A1
WO2022257993A1 PCT/CN2022/097721 CN2022097721W WO2022257993A1 WO 2022257993 A1 WO2022257993 A1 WO 2022257993A1 CN 2022097721 W CN2022097721 W CN 2022097721W WO 2022257993 A1 WO2022257993 A1 WO 2022257993A1
Authority
WO
WIPO (PCT)
Prior art keywords
water
heat exchange
exchange part
heat
temperature
Prior art date
Application number
PCT/CN2022/097721
Other languages
English (en)
Chinese (zh)
Inventor
李东哲
王远鹏
左计学
夏兴祥
陈卫星
潘翠连
管清杭
李守山
王庆波
傅华
Original Assignee
青岛海信日立空调系统有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN202110639064.6A external-priority patent/CN113531935A/zh
Priority claimed from CN202110709626.XA external-priority patent/CN113432172A/zh
Priority claimed from CN202123050748.7U external-priority patent/CN216521915U/zh
Priority claimed from CN202210374161.1A external-priority patent/CN114659294B/zh
Application filed by 青岛海信日立空调系统有限公司 filed Critical 青岛海信日立空调系统有限公司
Priority to CN202280008879.7A priority Critical patent/CN116670436A/zh
Priority to EP22819590.5A priority patent/EP4354048A1/fr
Publication of WO2022257993A1 publication Critical patent/WO2022257993A1/fr

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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1066—Arrangement or mounting of control or safety devices for water heating systems for the combination of central heating and domestic hot water
    • F24D19/1072—Arrangement or mounting of control or safety devices for water heating systems for the combination of central heating and domestic hot water the system uses a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
    • F24D3/105—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system pumps combined with multiple way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0096—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater combined with domestic apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/104—Inspection; Diagnosis; Trial operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/136—Defrosting or de-icing; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/212—Temperature of the water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/238—Flow rate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/242—Pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/305—Control of valves
    • F24H15/31—Control of valves of valves having only one inlet port and one outlet port, e.g. flow rate regulating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/305—Control of valves
    • F24H15/32—Control of valves of switching valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/335—Control of pumps, e.g. on-off control
    • F24H15/34—Control of the speed of pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/40—Control of fluid heaters characterised by the type of controllers
    • F24H15/414—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based
    • F24H15/421—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based using pre-stored data
    • F24H15/429—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based using pre-stored data for selecting operation modes
    • 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
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0046—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground
    • F24F2005/0064—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground using solar energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0046—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground
    • 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
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • 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
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series 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
    • F25B2313/031—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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2600/2519—On-off 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
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet of the condenser
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—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
    • 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

Definitions

  • the present disclosure relates to the technical field of heat pumps, in particular to a heat pump system and a control method thereof.
  • the heat pump system uses electric energy as the driving force, and uses outdoor ambient air as a heat source to provide heat to the regulated object. Compared with electric water heaters and gas water heaters, it has the characteristics of high energy efficiency and low energy consumption, so it has received widespread attention in the industry.
  • the heat pump system includes at least one heat pump indoor unit including a cascade heat exchanger and a terminal heat exchanger assembly.
  • the cascade heat exchanger includes: a first heat exchange part and a second heat exchange part, the first heat exchange part is connected to a low-temperature stage circulation pipeline, and there is a first refrigerant in the low-temperature stage circulation pipeline; the second heat exchange part The high-temperature stage circulation pipeline is connected, and there is a second refrigerant in the high-temperature stage circulation pipeline, and the second heat exchange part is configured to perform heat exchange with the first heat exchange part.
  • the terminal heat exchanger assembly includes: the third heat exchange part, the fourth heat exchange part and the terminal heat exchange part, the third heat exchange part is connected to the low-temperature grade circulation pipeline; the fourth heat exchange part is connected to the high-temperature grade The heat part is connected to the indoor terminal equipment, and the terminal heat exchange part is configured to perform heat exchange with the third heat exchange part, or to perform heat exchange with the fourth heat exchange part, or to perform heat exchange with the third heat exchange part and the fourth heat exchange part. part for heat exchange.
  • some embodiments of the present application provide a control method for the above heat pump system.
  • the heat pump system is any heat pump system described in the above-mentioned embodiments, and the control method of the heat pump system includes: determining whether the heat pump system meets preset conditions, and the preset conditions include low-temperature heating conditions, defrosting conditions, and high-temperature heating conditions.
  • the control terminal heat exchange part performs heat exchange with the third heat exchange part; if the heat pump system meets high-temperature heating conditions, the control terminal heat exchange part and the third heat exchange part
  • the fourth heat exchange part performs heat exchange; if the heat pump system meets the rapid heating condition, the control terminal heat exchange part performs heat exchange with the third heat exchange part and the fourth heat exchange part.
  • FIG. 1 is a block diagram of a heat pump system according to some embodiments
  • FIG. 2 is a block diagram of another heat pump system according to some embodiments.
  • Fig. 3 is a schematic diagram of refrigerant circulation when the heat pump system works in a low-temperature heating mode according to some embodiments
  • Fig. 4 is a schematic diagram of refrigerant circulation when the heat pump system works in the defrosting mode according to some embodiments
  • Fig. 5A is a schematic diagram of refrigerant circulation when the heat pump system works in a high-temperature heating mode according to some embodiments
  • Fig. 5B is a schematic diagram of refrigerant circulation when the heat pump system works in the fast heating mode according to some embodiments
  • Figure 6A is a block diagram of yet another heat pump system according to some embodiments.
  • Fig. 6B is a schematic diagram of refrigerant circulation when the heat pump system works in a high-temperature heating mode according to some embodiments
  • Fig. 7 is a structural diagram of another heat pump system according to some embodiments.
  • Fig. 8 is a structural diagram of another heat pump system according to some embodiments.
  • Fig. 9 is a structural diagram of another heat pump system according to some embodiments.
  • Fig. 10 is a working principle diagram of producing medium-temperature water by a heat pump system according to some embodiments.
  • Fig. 11 is a working principle diagram of the heat pump system producing high-temperature water according to some embodiments.
  • Figure 12 is a schematic diagram of the working principle of defrosting a heat pump system according to some embodiments.
  • FIG. 13 is a block diagram of yet another heat pump system according to some embodiments.
  • Fig. 14 is a structural diagram of a one-to-one heat pump system according to some embodiments.
  • Fig. 15 is a structural diagram of a one-drag-multi-connection heat pump system according to some embodiments.
  • Fig. 16 is a structural diagram of another one-drag-multi-connection heat pump system according to some embodiments.
  • Fig. 17 is a structural diagram of another one-drag-multi-connection heat pump system according to some embodiments.
  • FIG. 18 is a block diagram of yet another heat pump system according to some embodiments.
  • Fig. 19 is a working principle diagram of a relay reversing device according to some embodiments.
  • Fig. 20 is a working principle diagram of another relay reversing device according to some embodiments.
  • FIG. 21 is a block diagram of yet another heat pump system according to some embodiments.
  • 22 is a flow chart of water pump emptying control prior to water pump characterization testing of a heat pump system according to some embodiments
  • FIG. 23 is a flow chart of a heat pump system performing a water pump characteristic test according to some embodiments.
  • 24 is a graph of a water pump characterization test of a heat pump system according to some embodiments.
  • FIG. 25 is a flow chart of water pump emptying control prior to pipeline characteristic testing of the heat pump system according to some embodiments.
  • Fig. 26 is a flowchart of a heat pump system performing a pipeline characteristic test according to some embodiments.
  • Figure 27 is a graph of a piping characterization test of a heat pump system according to some embodiments.
  • Fig. 28 is a flowchart of constant speed control of a heat pump system according to some embodiments.
  • 29 is a graph of a water pump-pipe characteristic test of a heat pump system according to some embodiments.
  • Fig. 30 is a flowchart of constant flow control of a heat pump system according to some embodiments.
  • Fig. 31 is a flowchart of constant temperature difference control of a heat pump system according to some embodiments.
  • Fig. 32 is a flowchart of a control method of a heat pump system according to some embodiments.
  • the heat pump system can use outdoor ambient air or other media as a heat source, and use a compressor, condenser, throttling device, and evaporator to perform a refrigerant cycle to provide heat to indoor terminal equipment.
  • the present disclosure does not limit the type of the heat pump system, and the following embodiments take the heat pump system as an example of an air source heat pump for illustration.
  • the cascade heat pump system includes a low-temperature circulation system and a high-temperature circulation system.
  • the low-temperature circulation system and the high-temperature circulation system work simultaneously to produce high-temperature hot water.
  • the flexibility of the cascade heat pump system is poor.
  • the cascade heat pump system must also start the low-temperature stage circulation system and the high-temperature stage circulation system at the same time, which will cause the high-temperature stage circulation system to fail to generate sufficient pressure. Poor, the pressure ratio deviates from the normal operating range, which is not conducive to the reliable operation of the high-temperature circulation system.
  • the set water temperature is low, starting the high-temperature stage circulation system will cause high energy consumption of the cascade heat pump system.
  • the heat pump system includes a heat pump indoor unit 10 .
  • the heat pump indoor unit 10 includes a cascade heat exchanger 11 and a terminal heat exchanger assembly 16 .
  • the cascade heat exchanger 11 includes a first heat exchange portion 12 and a second heat exchange portion 14 .
  • the first heat exchange part 12 is connected to a low-temperature stage circulation pipeline 13, and the low-temperature stage circulation pipeline 13 has a first refrigerant in it.
  • the second heat exchange part 14 is connected to the high temperature stage circulation pipeline 15 , the high temperature stage circulation pipeline 15 has a second refrigerant, and the second heat exchange part 14 is configured to exchange heat with the first heat exchange part 12 .
  • the cascade heat exchanger 11 may also be called an evaporative condenser.
  • the functions of the first heat exchange part 12 and the second heat exchange part 14 in the cascade heat exchanger 11 are different.
  • the first refrigerant in the first heat exchange part 12 condenses and releases heat, and the second refrigerant in the second heat exchange part 14 absorbs the heat released by the first refrigerant in the first heat exchange part 12 ;
  • the first refrigerant in the first heat exchange part 12 evaporates and absorbs heat, and the second refrigerant in the second heat exchange part 14 exchanges heat with the first refrigerant in the first heat exchange part 12 .
  • first refrigerant and the second refrigerant may be the same or different.
  • first refrigerant and the second refrigerant may be any one of R410A, R134a, R12, R22, R32, R290, R744 and other refrigerants respectively.
  • the following embodiments are illustrated by taking the first refrigerant as R410A and the second refrigerant as R134a as an example.
  • the terminal heat exchanger assembly 16 includes a terminal heat exchange part 17 , a third heat exchange part 18 and a fourth heat exchange part 19 .
  • the third heat exchange part 18 is connected to the low-temperature stage circulation pipeline 13
  • the fourth heat exchange part 19 is connected to the high-temperature stage circulation pipe 15
  • the terminal heat exchange part 17 is connected to the indoor terminal equipment.
  • the terminal heat exchange part 17 includes a medium to be heated, and the medium to be heated is mainly water.
  • the indoor terminal device can be a water terminal, such as floor heating, radiator or water heater.
  • the terminal heat exchange part 17 is configured to perform heat exchange with the third heat exchange part 18, or to perform heat exchange with the fourth heat exchange part 19, or to perform heat exchange with the third heat exchange part 18 and the fourth heat exchange part 19. exchange.
  • the working modes of the heat pump system include but not limited to heating mode and cooling mode.
  • the heating modes include but not limited to low temperature heating mode, high temperature heating mode and fast heating mode.
  • Cooling modes include, but are not limited to, defrost modes.
  • the heat pump system works in the low-temperature heating mode; the low-temperature heating condition includes but is not limited to that the set temperature (such as the water temperature required by the user) is lower than the first preset temperature, and the low-temperature heating mode can be Prepare medium-warm water.
  • the heat pump system works in the high-temperature heating mode; the high-temperature heating conditions include but are not limited to the set temperature higher than the third preset temperature, and the high-temperature heating mode can produce high-temperature water.
  • the heat pump system meets the defrosting condition, the heat pump system works in the defrosting mode; the defrosting condition includes but is not limited to that the temperature of the terminal heat exchange part 17 is higher than the second preset temperature.
  • the heat pump system meets the fast heating conditions, the heat pump system works in the fast heating mode, and the fast heating mode can also produce high-temperature water.
  • the fast heating mode means that the heat pump system needs to heat up to the fourth preset temperature in a short time.
  • the indoor terminal device is a water heater
  • the heat pump system needs to complete heating in a short time. , so the heat pump system enters the rapid heating mode.
  • the working mode of the heat pump system is related to the parameters sent by the user, the temperature of the water entering the terminal heat exchange part 17 and other parameters. For example, if an instruction to enter the rapid heating mode is received from the user and the temperature of the water entering the water circulation circuit is relatively low, the heat pump system enters the rapid heating mode. For another example, if a defrosting instruction sent by a user is received, the heat pump system enters a defrosting mode.
  • lower includes less than or equal to, and higher includes greater than or equal to.
  • the first preset temperature may be less than or equal to the third preset temperature.
  • the embodiment of the present disclosure does not limit the values of the first preset temperature, the second preset temperature, the third preset temperature and the fourth preset temperature.
  • the low-temperature stage circulation system works, and the terminal heat exchange part 17 exchanges heat with the third heat exchange part 18 .
  • the high-temperature stage circulation system works, and the terminal heat exchange part 17 exchanges heat with the fourth heat exchange part 19 .
  • the heat pump system works in the fast heating mode, the low-temperature stage circulation system and the high-temperature stage circulation system work simultaneously, and the terminal heat exchange part 17 performs heat exchange with the third heat exchange part 18 and the fourth heat exchange part 19 at the same time, so as to Time to reach the temperature set by the user.
  • the low-temperature stage circulation system works, and the terminal heat exchange part 17 exchanges heat with the third heat exchange part 18 .
  • the difference between the heat pump system working in the defrosting mode and the low-temperature heating mode is that the flow direction of the first refrigerant in the defrosting mode is opposite to that in the low-temperature heating mode.
  • the heat pump system provided by the embodiments of the present disclosure does not need to start the high-temperature stage circulation system in the scene where the set water temperature is low, so as to avoid the problem that the high-temperature stage circulation system cannot generate sufficient pressure difference and cause low reliability of system operation. Ensure reliable operation of heat pump systems. Moreover, since the terminal heat exchange part 17 can also perform heat exchange with the third heat exchange part 18 connected to the low-temperature stage circulation pipeline and the fourth heat exchange part 19 connected to the high-temperature stage circulation pipeline, it can also meet the set water temperature. higher usage scenarios. Therefore, the heat pump system provided by the embodiments of the present disclosure has high flexibility and low energy consumption.
  • the heat pump system further includes a heat pump outdoor unit 1 , and the heat pump outdoor unit 1 and the heat pump indoor unit 10 together form a high-temperature stage circulation system and a low-temperature stage circulation system.
  • the heat pump outdoor unit 1 includes an outdoor heat exchanger 32 , a second compressor 30 and a four-way valve 31 , and the outdoor heat exchanger 32 , the second compressor 30 and the four-way valve 31 are connected through a low-temperature stage circulation pipeline 13 .
  • the outdoor heat exchanger 32 includes a finned tube heat exchanger.
  • the second compressor 30 may also be referred to as a low temperature stage compressor.
  • the second compressor 30 and the first compressor 33 may be the same or different.
  • the low-temperature stage circulation system includes a low-temperature stage circulation pipeline 13, and the low-temperature stage circulation pipeline 13 has a first refrigerant R410A.
  • the high temperature stage circulation system includes a high temperature stage circulation pipeline 15, and the high temperature stage circulation pipeline 15 has a second refrigerant R134a.
  • the heat pump indoor unit 10 may further include a first valve element 22, a second valve element 23 and a third valve element 24, by controlling the first valve element 22, the second valve element 23 and the third valve element
  • the connection and shutdown of 24 can realize whether the heat pump system configures whether the high-temperature stage circulation system works according to actual usage requirements.
  • the first valve element 22 is disposed between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13 , and the first valve element 22 is configured to regulate the flow of the first refrigerant entering the first heat exchange part 12 traffic.
  • the second valve element 23 is disposed between the second heat exchange portion 14 and the fourth heat exchange portion 19 , and the second valve element 23 is configured to regulate the second refrigeration flow entering the second heat exchange portion 14 and the fourth heat exchange portion 19 . agent flow.
  • the third valve element 24 is disposed between the third heat exchange portion 18 and the low-temperature stage circulation pipeline 13 , and the third valve element 24 is configured to regulate the flow of the first refrigerant entering the third heat exchange portion 18 .
  • valve elements eg, the first valve element 22 , the second valve element 23 , and the third valve element 24
  • the working states of the first valve element 22 , the second valve element 23 and the third valve element 24 may include, for example, a connected state, a closed state, a throttling state, and the like.
  • the heat pump indoor unit 10 further includes a first compressor 33 connected to the high temperature stage circulation pipeline 15 .
  • the first compressor 33 may also be referred to as a high temperature stage compressor.
  • the first compressor 33 stops (stops running).
  • the first valve element 22 is configured to work in a shut-off state, so as to shut off the passage between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13 .
  • the third valve element 24 is configured to work in an open state to communicate the passage between the third heat exchange part 18 and the low-temperature stage circulation pipeline 13 .
  • the first refrigerant in the outdoor heat exchanger 32 absorbs heat from the outdoor environment or other external media, evaporates and enters the second compressor 30 for compression to obtain a high-temperature and high-pressure gaseous first refrigerant, which enters the In the low-temperature stage circulation pipeline 13 of the heat pump system.
  • the first valve element 22 shuts off the refrigerant passage between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13
  • the first refrigerant cannot circulate through the first heat exchange part 12, but enters the first heat exchange part 12.
  • the medium such as water
  • the first refrigerant releases heat in the third heat exchange part 18, and heats the water in the terminal heat exchange part 17 to a set temperature to realize low-temperature stage heating of the heat pump system.
  • the first refrigerant finishes heating the medium in the terminal heat exchange part 17 it flows out from the third heat exchange part 18 , passes through the open third valve element 24 , and returns to the heat pump outdoor unit 1 .
  • the pressure is throttled back to the state of low temperature and low pressure.
  • the flow path of the first refrigerant is shown as F1 in FIG. 3 .
  • the outdoor heat exchanger 32 When the heat pump system works in the heating mode, the outdoor heat exchanger 32 is used as an evaporator, and when the outdoor temperature is low, frosting may occur on the outdoor heat exchanger 32 .
  • the medium in the terminal heat exchange part 17 can transfer heat to the third heat exchange part 18, so as to increase the temperature of the first refrigerant and improve the defrosting of the outdoor heat exchanger 32. speed, thereby improving the heating effect of the heat pump system.
  • the heat pump system when the temperature of the terminal heat exchange part 17 is higher than the second preset temperature, the heat pump system can work in the defrosting mode. For example, when the temperature of the terminal heat exchange part 17 is greater than or equal to 8° C., the heat pump system works in the defrosting mode. Wherein, the temperature of the terminal heat exchange part 17 includes the temperature of water or other medium in the terminal heat exchange part 17 .
  • a heat pump system may be operated in a defrost mode periodically. For example, if the temperature of the terminal heat exchange part 17 is greater than or equal to 8° C. every 48 hours, the heat pump system enters the defrosting mode.
  • the first compressor 33 stops running.
  • the first valve element 22 is configured to work in a shut-off state, so as to shut off the passage between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13 .
  • the third valve element 24 is configured to operate in a throttled state.
  • the four-way valve 31 in the low temperature stage circulation system changes direction.
  • the first refrigerant in the third heat exchange part 18 exchanges heat with the water in the terminal heat exchange part 17 , and evaporates after absorbing heat.
  • the first valve element 22 shuts off the passage between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13
  • the first refrigerant after absorbing heat cannot enter the low-temperature stage circulation pipeline through the cascade heat exchanger 11 13, but after being compressed in the second compressor 30, it flows into the outdoor heat exchanger 32, where heat is released in the outdoor heat exchanger 32 to complete defrosting.
  • the third valve element 24 in the throttling state returns to the terminal heat exchange portion 17 .
  • the flow path of the first refrigerant is shown as F3 in FIG. 4 .
  • the defrost mode may also be referred to as a reverse cycle defrost mode.
  • the first compressor 33 runs.
  • the first valve element 22 is configured to work in an open state to communicate the passage between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13 .
  • the second valve element 23 is configured to work in a throttling state to communicate the passage between the second heat exchange part 14 and the fourth heat exchange part 19 .
  • the third valve element 24 is configured to work in a shut-off state to shut off the passage between the third heat exchange part 18 and the low-temperature stage circulation pipeline 13 .
  • the first refrigerant in the outdoor heat exchanger 32 absorbs heat from the outdoor environment or other external media, evaporates and enters the second compressor 30 for compression, and the obtained high-temperature and high-pressure gaseous first refrigerant enters the cascade heat exchanger 11
  • the first heat exchange part 12 in.
  • the first heat exchange part 12 works in a condensation state
  • the second heat exchange part 14 works in an evaporation state.
  • the second refrigerant in the second heat exchange part 14 absorbs the heat released by the first refrigerant in the first heat exchange part 12, it evaporates and enters the first compressor 33 for compression, and the obtained high-temperature and high-pressure gaseous second refrigeration
  • the agent enters the fourth heat exchange part 19, exchanges heat with the water in the terminal heat exchange part 17, heats the water in the terminal heat exchange part 17 to the set temperature, and realizes high-temperature heating of the heat pump system.
  • the flow path of the first refrigerant is shown as F1 in FIG. 5A
  • the flow path of the second refrigerant is shown as F2 in FIG. 5A .
  • the first valve element 22 when the heat pump system works in the rapid heating mode, the first valve element 22 is configured to work in an open state to communicate the passage between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13 .
  • the second valve element 23 is configured to work in a throttling state to communicate the passage between the second heat exchange part 14 and the fourth heat exchange part 19 .
  • the third valve element 24 is configured to work in an open state to communicate the passage between the third heat exchange part 18 and the low-temperature stage circulation pipeline 13 .
  • the difference between the heat pump system working in the fast heating mode and the heat pump system working in the high temperature heating mode is that when the heat pump system works in the fast heating mode, the third valve element 24 is configured to work in the open state, so the second compression
  • the high-temperature and high-pressure gaseous first refrigerant compressed by the machine 30 can either enter the first heat exchange part 12 of the cascade heat exchanger 11, or enter the third heat exchange part 18 to exchange heat with the terminal heat exchange part 17.
  • the working principle of the high temperature and high pressure gaseous first refrigerant entering the first heat exchange part 12 of the cascade heat exchanger 11 for heat exchange is the same as that of the heat pump system working in the high temperature heating mode, and will not be repeated here.
  • the high-temperature stage circulation system and the low-temperature stage circulation system can be used to heat the water in the terminal heat exchange part 17 at the same time, so as to achieve the purpose of rapid heating.
  • the flow path of the first refrigerant is shown as F1 in FIG. 5B
  • the flow path of the second refrigerant is shown as F2 in FIG. 5B .
  • corresponding cut-off valves (27, 28) and valves (25, 26) may also be provided at the connecting pipelines of the heat pump indoor unit 10 and the heat pump outdoor unit 1.
  • the terminal heat exchange part 17 may also be correspondingly provided with valves ( 20 , 21 ) or valves (not shown in FIG. 2 ) for controlling waterway connections.
  • the terminal heat exchange part 17 may further include a first sub-terminal heat exchange part 36 and a second sub-terminal heat exchange part 37 .
  • the first sub-terminal heat exchange part 36 communicates with the second sub-terminal heat exchange part 37 in series.
  • the terminal heat exchanger assembly 16 may include a first terminal heat exchanger 34 and a second terminal heat exchanger 35.
  • the first terminal heat exchanger 34 and the second terminal heat exchanger 35 may be made of water fluorine, for example.
  • the heat exchanger is realized.
  • the first terminal heat exchanger 34 includes a first sub-terminal heat exchange part 36 and a third heat exchange part 18, the water in the first sub-terminal heat exchange part 36 exchanges heat with the first refrigerant in the third heat exchange part 18 Exchange;
  • the second terminal heat exchanger 35 includes a second sub-terminal heat exchange part 37 and a fourth heat exchange part 19, the water in the second sub-terminal heat exchange part 37 and the second refrigeration in the fourth heat exchange part 19 agent for heat exchange.
  • the heat pump system can be used to produce high-temperature water, such as water higher than 60°C.
  • the working mode of the heat pump system is the high-temperature heating mode, and the first compressor 33 is running at this time.
  • the first valve element 22 is configured to work in an open state to communicate the passage between the first heat exchange part 12 and the low-temperature stage circulation pipeline 13 .
  • the second valve element 23 is configured to work in a throttling state to communicate the passage between the second heat exchange part 14 and the fourth heat exchange part 19 .
  • the third valve element 24 is configured to work in a disconnected state to disconnect the passage between the third heat exchange part 18 and the low-temperature stage circulation pipeline 13 .
  • the first refrigerant in the outdoor heat exchanger 32 absorbs heat from the outdoor environment or other external media, evaporates and enters the second compressor 30 to be compressed to form a high-temperature and high-pressure gaseous first refrigerant.
  • the high-temperature and high-pressure gaseous first refrigerant enters the first heat exchange part 12 .
  • the first heat exchange part 12 works in the condensation state
  • the second heat exchange part 14 works in the evaporation state
  • the second refrigerant in the second heat exchange part 14 and the first heat exchange part 12 The first refrigerant in the heat exchange, the second refrigerant absorbs heat and evaporates, and enters the first compressor 33 to be compressed after evaporation, forming a high-temperature and high-pressure gaseous second refrigerant that enters the fourth heat exchanger in the second terminal heat exchanger 36
  • the heat part 19 exchanges heat with the water in the second sub-terminal heat exchange part 37 to heat the water to a temperature above 60°C.
  • the flow path of the first refrigerant is shown as F4 in FIG. 6B
  • the flow path of the second refrigerant is shown as F5 in FIG. 6B .
  • the heat pump system shown in Figure 6A can also work in the low-temperature heating mode, defrosting mode and fast heating mode, and the working principle of the heat pump system when it works in the low-temperature heating mode, defrosting mode and fast heating mode can be referred to The relevant descriptions of the above-mentioned FIG. 3 , FIG. 4 and FIG. 5B will not be repeated here.
  • the second valve element 23 can also be connected to the first interface of the fourth heat exchange part 19 and the first interface of the second heat exchange part 14 respectively.
  • One end of the first compressor 33 is connected to the second interface of the fourth heat exchange part 19
  • the other end of the first compressor 33 is connected to the second interface of the second heat exchange part 14 .
  • the second valve element 23 , the fourth heat exchange part 19 , the first compressor 33 and the second heat exchange part 14 constitute a high temperature stage circulation system.
  • the heat pump outdoor unit 1 further includes a fourth valve element 104 .
  • both ends of the fourth valve element 104 are respectively connected to the first port of the third heat exchange part 18 and the first port of the outdoor heat exchanger 32;
  • the two ends are respectively connected to the second interface of the first heat exchange part 12 and the second interface of the outdoor heat exchanger 32;
  • the third end and the fourth end of the four-way valve 31 are respectively connected to the two ends of the second compressor 30;
  • the third The second interface of the heat exchange part 18 is connected to the second interface of the first heat exchange part 12 .
  • the fourth valve element 104 , the third heat exchange part 18 , the first heat exchange part 12 , the four-way valve 31 , the second compressor 30 and the outdoor heat exchanger 32 form a low-temperature stage circulation system.
  • both ends of the fourth valve element 104 are respectively connected to the second port of the first heat exchange part 12 and the first port of the outdoor heat exchanger 32 , and the first port of the four-way valve 31
  • the third end and the second end of the four-way valve 31 are respectively connected to the second port of the second compressor 30 and the second port of the outdoor heat exchanger 32.
  • the first interface of the third heat exchange part 18 is connected to the first interface of the first heat exchange part 12 .
  • the heat pump indoor unit 10 may further include a water inlet pipe, a water pump 402, a first electric three-way valve 401 and a water outlet pipe.
  • the inlet of the water pump 402 is connected to the water inlet pipe, and the outlet of the water pump 402 is connected to the inlet of the first electric three-way valve 401 .
  • the first outlet of the first electric three-way valve 401 is connected to the first interface of the first sub-terminal heat exchange part 36
  • the second outlet of the first electric three-way valve 401 is connected to the first interface of the second sub-terminal heat exchange part 37 .
  • Both the second interface of the first sub-terminal heat exchange part 36 and the second interface of the second sub-terminal heat exchange part 37 are connected to the water outlet pipe.
  • the inlet of the water pump 402 is connected to the water inlet pipe, and the outlet of the water pump 402 is connected to the first interface of the first sub-terminal heat exchange part 36 .
  • the second interface of the first sub-terminal heat exchange part 36 is connected to the inlet of the first electric three-way valve 401
  • the first outlet of the first electric three-way valve 401 is connected to the first interface of the second sub-terminal heat exchange part 37 .
  • Both the second interface of the second sub-terminal heat exchange part 37 and the second outlet of the first electric three-way valve 401 are connected to the water outlet pipe.
  • the heat pump system shown in FIG. 7 can also produce medium-temperature water and high-temperature water.
  • the temperature of the low-temperature water may be 40°C-60°C
  • the temperature of the high-temperature water may be 60°C-80°C.
  • the second compressor 30 runs, the first compressor 33 stops, the high-temperature stage circulation system does not operate, and the low-temperature stage circulation system operates.
  • the inlet of the first electric three-way valve 401 communicates with the first outlet of the first electric three-way valve 401 , that is, the first electric three-way valve 401 is in a straight-through state.
  • the water in the water inlet pipe flows into the first sub-terminal heat exchange part 36 through the water pump 402 .
  • the high-temperature and high-pressure gaseous first refrigerant compressed by the second compressor 30 passes through the first heat exchange part 12.
  • the first refrigerant does not flow through the cascade heat exchanger 11. heat exchange.
  • the first refrigerant enters the third heat exchange part 18 from the first heat exchange part 12, the first refrigerant exchanges heat with the water in the first sub-terminal heat exchange part 36 in the first terminal heat exchanger 34, so as to Prepare hot water at 40°C-60°C.
  • the arrows in Fig. 10 may represent the direction of heat transfer during the production of medium-temperature water.
  • the first compressor 33 and the second compressor 30 are running, and both the low-temperature stage circulation system and the high-temperature stage circulation system are in operation.
  • the inlet of the first electric three-way valve 401 communicates with the second outlet of the first electric three-way valve 401 , that is, the first electric three-way valve 401 is in a bend state.
  • the water in the water inlet pipe flows into the second sub-terminal heat exchange part 37 through the water pump 402 .
  • the high-temperature and high-pressure gaseous first refrigerant compressed by the second compressor 30 enters the first heat exchange part 12, and releases heat in the first heat exchange part 12; After the second refrigerant absorbs the heat released by the first heat exchange part 12 in the second heat exchange part 14, it enters the fourth heat exchange part 19, and the second refrigerant exchanges with the second sub-terminal in the first terminal heat exchanger 35.
  • the water in the heat section 37 is subjected to heat exchange to produce hot water at a temperature of 60°C-80°C.
  • the temperature of the high temperature water is related to the second refrigerant used in the high temperature stage circulation system.
  • the second refrigerant is R134a
  • the temperature of the high-temperature water can reach 80°C.
  • the arrows in Fig. 11 may represent the direction of heat transfer during the production of high-temperature water.
  • Fig. 12 is a working principle diagram of the heat pump system shown in Fig. 7 working in the defrosting mode. It can be seen from FIG. 7 and FIG. 12 that the working principle of the heat pump system shown in FIG. 7 when it works in the defrosting mode is similar to that when it works in the low-temperature heating mode. The difference is that, when the heat pump system shown in FIG. 7 works in the defrosting mode, the flow direction of the first refrigerant is opposite to that in the low-temperature heating mode.
  • the arrows in Fig. 12 may represent the direction of heat transfer in the defrosting mode.
  • the heat pump systems shown in Figures 8 and 9 can also work in low-temperature heating mode, defrosting mode, high-temperature heating mode and rapid heating mode, and the heat pump systems shown in Figures 7 to 9 work in different modes
  • the heat pump indoor unit may further include a temperature sensing component.
  • the temperature sensing component is configured to detect the temperature of the medium in the terminal heat exchange part 17 .
  • the heat pump system is configured to work in a low-temperature heating mode, a defrosting mode, a high-temperature heating mode, or a rapid heating mode in response to the temperature of the medium in the terminal heat exchange portion 17 detected by the temperature sensing component.
  • the temperature sensing assembly may include a first temperature sensor 301, a second temperature sensor 302, a third temperature sensor 303, a fourth temperature sensor 304, a fifth temperature sensor 305, a sixth temperature sensor 403, a seventh temperature sensor temperature sensor 404 .
  • the first temperature sensor 301 is arranged between the four-way valve 31 and the first heat exchange part 12, the second temperature sensor 302 is arranged between the first heat exchange part 12 and the third heat exchange part 18, and the third temperature sensor 303 is arranged Between the third heat exchange part 18 and the fourth valve element 104 .
  • the fourth temperature sensor 304 is set at the outlet of the first compressor 33, the fifth temperature sensor 305 is set between the fourth heat exchange part 19 and the second valve element 23, and the sixth temperature sensor 403 is set between the water pump 402 and the first motor Between the three-way valves 401, the seventh temperature sensor 404 is arranged in the water outlet pipeline.
  • the fourth valve element 104 may include an indoor valve element 1041 and an outdoor valve element 1042 .
  • the second compressor 30, the four-way valve 31, the outdoor heat exchanger 32 and the outdoor valve element 1042 can be installed in the heat pump outdoor unit 1; the water pump 402, the first electric three-way valve 401, the cascade heat exchange part 11, the terminal
  • the heat exchange assembly 16 , the second valve element 23 , the first compressor 33 and the indoor valve element 1041 may be disposed on the heat pump indoor unit 10 .
  • the heat pump system may include one heat pump indoor unit 10 or multiple heat pump indoor units 10 .
  • the heat pump indoor unit 10 and the heat pump outdoor unit 1 form a one-to-one heat pump system.
  • the heat pump system includes a plurality of heat pump indoor units 10
  • the plurality of heat pump indoor units 10 and the heat pump outdoor unit 1 form a one-to-many heat pump system.
  • the heat pump indoor unit 10 can also be connected to the same heat pump outdoor unit 1 with other indoor units (such as indoor units for ambient temperature adjustment) to form a one-drag multi-unit heat pump system.
  • other indoor units may be at least one air-cooled indoor unit 2 , and the at least one air-cooled indoor unit 2 is connected to the heat pump outdoor unit 1 together with the heat pump indoor unit 10 .
  • the heat pump indoor unit 10 further includes a relay reversing device 201 , a buffer water tank 202 and indoor terminal devices 205 , 206 , and 207 .
  • the indoor terminal devices 205, 206, 207 include a domestic hot water tank and at least one space heating/cooling device, and at least two of the indoor terminal devices 205, 206, 207 are switched to operate.
  • the buffer water tank 202 includes a first water inlet A', a first water outlet B, a first water return port C and a second water outlet D.
  • the relay reversing device 201 has a second water inlet A' connected to the water outlet of the terminal heat exchange part 17, a third water outlet B' connected to the water return port of the terminal heat exchange part 17, and a water outlet connected to the indoor terminal equipment 205, 206, 207.
  • the second water return port C' and the fourth water outlet D' connected by the main pipeline.
  • the relay reversing device 201 also includes a first straight branch, a first bypass branch, a second straight branch and a second bypass branch.
  • the first straight branch directly communicates with the second water inlet A' and the fourth water outlet D'.
  • the first bypass branch includes a first sub-bypass branch and a second sub-bypass branch.
  • the first sub-bypass branch is connected to the second water inlet A' and the first water inlet A
  • the second sub-bypass branch is connected to the first water outlet B and the fourth water outlet D'.
  • the first straight branch is switched and communicated with the first bypass branch to realize the communication pipeline from the terminal heat exchange part 17 to the indoor terminal equipment 205, 206, 207.
  • the second straight branch directly connects the second water return port C' and the third water outlet B'.
  • the second bypass branch includes a third sub-bypass branch and a fourth sub-bypass branch.
  • the third sub-bypass branch is connected to the second water return port C' and the first water return port C
  • the fourth sub-bypass branch is connected to the second water outlet D and the third water outlet B'.
  • the second straight-through branch and the second bypass branch are switched and communicated to realize the communication pipeline from the indoor terminal equipment 205 , 206 , 207 to the terminal heat exchange part 17 .
  • the relay reversing device 201 can switch between the direct branch and the bypass branch through multiple electric three-way valves or multiple one-way valves.
  • the relay reversing device 201 includes a second electric three-way valve 2011 , a third electric three-way valve 2012 , a fourth electric three-way valve 2013 and a fifth electric three-way valve 2014 .
  • the first end of the second electric three-way valve 2011 communicates with the second water inlet A'
  • the second end of the second electric three-way valve 2011 communicates with the first end of the third electric three-way valve 2012
  • the third electric three-way valve The second end of the valve 2012 communicates with the fourth water outlet D'
  • the third end of the second electric three-way valve 2011 communicates with the first water inlet A
  • the third end of the third electric three-way valve 2012 communicates with the first water outlet B is connected.
  • the first end of the second electric three-way valve 2011 communicates with the second end of the second electric three-way valve 2011, and the first end of the third electric three-way valve 2012 communicates with the third electric three-way valve.
  • a first straight branch is formed. At this time, the water flowing out of the water outlet of the terminal heat exchange part 17 flows to the indoor terminal equipment sides 205 , 206 , and 207 through the first straight branch.
  • the first end of the fourth electric three-way valve 2013 communicates with the third water outlet B'
  • the second end of the fourth electric three-way valve 2013 communicates with the first end of the fifth electric three-way valve 2014
  • the fifth The second end of the electric three-way valve 2014 communicates with the second water return port C'
  • the third end of the fourth electric three-way valve 2013 communicates with the second water outlet D
  • the third end of the fifth electric three-way valve 2014 communicates with the second water outlet.
  • a return port C is connected.
  • the first end of the fourth electric three-way valve 2013 and the second end of the fourth electric three-way valve 2013 are connected, and the first end of the fifth electric three-way valve 2014 is connected to the fifth electric three-way valve.
  • a second straight branch is formed.
  • the return water on the side of the indoor terminal equipment 205 , 206 , and 207 flows back to the return water port of the terminal heat exchange part 17 through the second straight branch.
  • the dotted line arrow when the first end of the fourth electric three-way valve 2013 and the third end of the fourth electric three-way valve 2013 are connected, the third sub-bypass branch is formed; in the fifth electric three-way valve 2014 When the second end of the valve is connected with the third end of the fifth electric three-way valve 2014, a fourth sub-bypass branch is formed. At this time, the return water from the indoor terminal equipment 205, 206, 207 side flows back to the return water port of the terminal heat exchange part 17 through the fourth sub-bypass branch, the buffer water tank 202 and the third sub-bypass branch.
  • connection of the second through branch when controlling the connection of the first through branch, the connection of the second through branch must also be controlled; when controlling the connection of the first bypass branch, correspondingly, the connection of the second bypass branch must be controlled.
  • the relay reversing device 201 can also realize switching between the direct branch and the bypass branch through a plurality of one-way valves.
  • the relay reversing device 201 may include a first one-way valve, a second one-way valve, and a third one-way valve.
  • the first end of the first one-way valve is respectively connected to the second water inlet A' and one end of the second one-way valve, and the other end of the first one-way valve is respectively connected to the fourth water outlet D' and one end of the third one-way valve , the other end of the second one-way valve is connected to the first water inlet A, and the other end of the third one-way valve is connected to the first water outlet B.
  • the first straight branch is connected; when the second one-way valve is closed, the first sub-bypass branch is closed, and when the third one-way valve is closed, the second sub-bypass branch is closed .
  • multiple one-way valves can also be used to construct the second straight-through branch, the third sub-bypass branch and the fourth sub-bypass branch, which will not be repeated here.
  • the relay reversing device further includes a first booster pump 2015 and a second booster pump 2016 .
  • the first booster pump 2015 is arranged on the pipeline between the second water inlet A' and the second electric three-way valve 2011 to increase the pressure of the water in the pipeline.
  • the second booster pump 2016 is arranged on the pipeline between the third electric three-way valve 2012 and the fourth water outlet D' to increase the pressure of the water in the pipeline.
  • the domestic hot water tank 206 and the space heating/cooling equipment 205, 207 may belong to different types of indoor terminal equipment.
  • the domestic hot water tank 206 is in the heating mode when running; and the space heating/cooling equipment 205, 207 can be in the heating mode or in the cooling mode when running.
  • an electric three-way valve may be used among the indoor terminal devices 205, 206, and 207 to realize switching operation. As shown in FIG. 18 , the switching operation between the domestic hot water tank 206 and the two space heating/cooling devices 205 and 207 can be realized through the electric three-way valve 203 and the electric three-way valve 204 .
  • the first end of the electric three-way valve 203 communicates with the fourth water outlet D'
  • the second end of the electric three-way valve 203 communicates with the water inlet side of the wind disc 205
  • the third end of the electric three-way valve 203 communicates with the electric three-way valve.
  • the first end of 204 communicates; the second end of electric three-way valve 204 communicates with the water inlet side of domestic hot water tank 206 , and the third end of electric three-way valve 204 communicates with the water inlet side of floor heating 207 .
  • an electric three-way valve can be added correspondingly, and the adjacent ports of the electric three-way valves are connected to each other.
  • multiple one-way valves can also be configured to configure the switching operation among the indoor terminal devices 205, 206, 207, which will not be repeated here.
  • the buffer water tank 202 can be used as a thermal storage device or a cold storage device.
  • the buffer water tank 202 is used as heat storage equipment
  • the relay reversing device 201 By collecting the temperature of the water in the indoor terminal equipment 205, 206, 207 and the target temperature, the relay reversing device 201 is controlled so that the water flowing out of the water outlet of the terminal heat exchange part 17 passes or does not pass through the buffer water tank 202 for heat exchange.
  • the control of the relay reversing device 201 can be controlled by the heat pump indoor unit 10, or can be controlled by an independent controller.
  • the independent controller control can prevent the buffer water tank 202 from communicating with the auxiliary heat source when the heat pump indoor unit 10 fails, so as to provide heat source for the indoor terminal equipment 205 , 206 , 207 .
  • the auxiliary heat source can be, for example, a gas wall-hung boiler, a solar water heater, or a gas water heater.
  • the relay reversing device 201 When the temperature difference between the water temperature and the target temperature in the indoor terminal equipment 205, 206, 207 is within the preset temperature range (for example -5°C ⁇ 5°C), control the relay reversing device 201 so that the first bypass branch and the buffer water tank 202 connected (the first straight branch is disconnected), at this time, the heat of the water in the buffer water tank 202 is used to provide heat sources for the indoor terminal devices 205, 206, 207. In the case of heating and the water temperature fluctuates little, using the heat in the buffer water tank 202 can ensure the temperature stability during space heating and improve user comfort.
  • the preset temperature range for example -5°C ⁇ 5°C
  • the relay reversing device 201 is controlled to connect the first straight branch, and the water flowing out of the water outlet of the terminal heat exchange part 17 does not pass through the buffer water tank 202, and utilizes the heat pump system
  • the cooling capacity is used to realize the cooling of the space heating/cooling equipment 205, 207, and reduce the pressure of the buffer water tank 202.
  • the relay reversing device 201 In the automatic operation mode, when the cooling of the space heating/refrigeration equipment 205, 207 is switched to the heating operation of the domestic hot water tank 206, the relay reversing device 201 is controlled to make the first straight branch connected, and the terminal heat exchange part The water that the water outlet of 17 flows out does not pass through buffer water tank 202, avoids that the water in buffer water tank 202 changes from cold water to hot water state or from hot water to cold water state, reduces buffer water tank 202 loads, has avoided energy waste simultaneously.
  • the heat pump system may further include an auxiliary heat source 102 for providing heat for the buffer water tank 202 .
  • the auxiliary heat source 102 and the heat pump system jointly provide heat for the water in the buffer water tank 202 .
  • the auxiliary heat source 102 communicates with the buffer tank 202 through a connecting pipeline.
  • the buffer water tank 202 is used as heat storage equipment, the auxiliary heat source 102 works, and the start and stop of the auxiliary heat source 102 can be controlled by the heat pump system.
  • the target temperature of the buffer water tank 202 can be changed according to the indoor terminal equipment 205, 206, 207.
  • the auxiliary heat source 102 and the heat pump indoor The unit 10 can jointly provide heat for the water in the buffer water tank 202 .
  • the auxiliary heat source 102 is a solar water heater
  • the water in the buffer water tank 202 can be heated if the solar heating temperature condition is satisfied, and the energy is effectively used.
  • the heat pump system may further include an alarm device.
  • the alarm device can issue an alarm to remind the user in time.
  • the cooling mode cannot be performed, but the heating mode can enter the emergency operation mode, and the auxiliary heat source 102 can be used to heat the water in the buffer water tank 202, and Further, the heating demands of the indoor terminal devices 205, 206, and 207 are met.
  • the buffer water tank 202 is used as cold storage equipment
  • the relay reversing device 201 When the space heating/refrigerating equipment 205, 207 is cooling, the relay reversing device 201 is controlled to make the first bypass branch communicate with the buffer water tank 202, and the water flowing out of the water outlet of the terminal heat exchange part 17 passes through the buffer water tank 202 to utilize the buffer water tank 202.
  • the cold storage capacity of the water tank 202 keeps the water temperature at a low level for a long time, improving user comfort.
  • the relay reversing device 201 When the domestic hot water tank 206 is heating, the relay reversing device 201 is controlled to make the first straight branch communicate, and the water flowing out of the water outlet of the terminal heat exchange part 17 does not pass through the buffer water tank 202, so as to avoid the water in the buffer water tank 202. The water is changed from cold water to hot water, so as to reduce the load of the buffer tank 202 and avoid energy waste at the same time.
  • the space heating/cooling devices are switched to operate.
  • the space heating/refrigeration equipment 205 wind tray
  • the space heating/refrigeration equipment 207 floor heating
  • switch operation if the buffer water tank 202 is used as heat storage equipment, for example, in winter, the floor heating 207 and the wind The heating switching process of the disk 205 is as described in (1-1), and will not be repeated here. If the buffer water tank is used as a cold storage device, for example, in summer or a transitional season, one of the wind disk 205 and the floor heating 207 is selected for cooling.
  • the relay reversing device 201 is controlled so that the first bypass branch communicates with the buffer water tank 202, and the water flowing out of the water outlet of the terminal heat exchange part passes through the buffer water tank 202, making full use of the cold storage capacity in the buffer water tank 202, so that the system The internal water temperature remains low for a long time, improving user comfort.
  • the working process of switching them is similar to the above, and will not be repeated here.
  • Some embodiments provided by the present disclosure can effectively reduce the pressure of the buffer water tank 202 while meeting the different requirements of the indoor terminal equipment 205, 206, 207, reduce energy loss and effectively improve user experience. .
  • the heat pump indoor unit 10 may also include a pressure detection device, a flow detection device, a temperature detection device, a water pump self-circulation pipeline, a water system Full cycle lines and controllers.
  • the pressure detection device is used to detect the upstream pressure and downstream pressure of the water pump 402.
  • the pressure detection device includes a water pressure sensor 8-2 for detecting the upstream pressure of the water pump 402 and a water pressure sensor 8-2 for detecting the downstream pressure of the water pump 402. Sensor 8-1.
  • the flow detecting device includes a water flow meter 9 for detecting the flow passing through the water pump 402 .
  • the water pump self-circulation pipeline includes a water pump 402 and an electric regulating valve 5 .
  • the full circulation pipeline of the water system includes a water pump 402, an indoor heat exchanger 32 and indoor terminal equipment. That is, the water pump 402 is shared by the self-circulation pipeline of the water pump and the full circulation pipeline of the water system.
  • the water pump 402 can be a variable frequency water pump.
  • the controller is coupled to the pressure detection device and the flow detection device, and is configured to perform a water pump characteristic test through the water pump self-circulation pipeline based on at least one of the upstream pressure of the water pump, the downstream pressure of the water pump, or the flow rate of the water pump, and pass the The full circulation pipeline of the water system is tested for pipeline characteristics.
  • the switching between the self-circulation pipeline of the water pump and the full circulation pipeline of the water system can be realized through the sixth electric three-way valve.
  • the sixth electric three-way valve may include an electric three-way valve 3-1 and an electric three-way valve 3-2.
  • the heat pump indoor unit 10 further includes a temperature detection device for detecting the outlet water temperature and the return water temperature of the terminal heat exchange part 17 .
  • the temperature detection device may include, for example, an outlet water temperature sensor 501 and a return water temperature sensor 502 .
  • the heat pump indoor unit 10 also includes an automatic exhaust valve 6-1 and a safety valve 7-1 located in the full circulation pipeline of the water system, and an automatic exhaust valve 6-2 and a safety valve located in the self-circulation pipeline of the water pump. Valve 7-2.
  • the full circulation pipeline of the water system includes a water pump 402, a water pressure sensor 8-1, an electric three-way valve 3-1, an indoor heat exchanger 32, and an automatic exhaust valve 6-1 connected in sequence through the pipeline. , safety valve 7-1, outlet water temperature sensor 501, indoor terminal equipment, return water temperature sensor 502, electric three-way valve 3-2, water flow meter 9, water pressure sensor 8-2.
  • the self-circulation pipeline of the water pump includes a water pump 402, a water pressure sensor 8-1, an electric three-way valve 3-1, an automatic exhaust valve 6-2, a safety valve 7-2, an electric regulating valve 5, and an electric valve connected sequentially through the pipeline.
  • the water pump 402 can realize automatic adjustment of different rotation speeds according to control input parameters.
  • the electric three-way valve 3-1 and the electric three-way valve 3-2 can switch between different pipelines according to the control signal, so as to realize the conversion of waterways.
  • the electric control valve 5 can have multiple opening adjustment functions.
  • Automatic exhaust valve 6-1 and automatic exhaust valve 6-2 can release excess air in the pipeline.
  • the safety valve 7-1 and the safety valve 7-2 release the pressure when the pipeline pressure exceeds the limit value, so as to play a protective role.
  • the water pressure sensor 8-1 and the water pressure sensor 8-2 can collect the water pressure downstream and upstream of the water pump 402 for resistance measurement.
  • the water flow meter 9 can measure the water flow into and out of the water pump 402 .
  • the outlet water temperature sensor 501 and the return water temperature sensor 502 are used to detect the temperature of the outlet water and return water of the terminal heat exchange part 17, and participate in the adjustment of the speed of the water pump during the constant temperature difference control.
  • the self-circulation pipeline of the water pump and the full circulation pipeline of the water system respectively include a first water supply port and a second water supply port.
  • the first water replenishment port includes water replenishment port 1
  • the second water replenishment port includes water replenishment port 2 .
  • the water supply port 1 is located between the water pump 402 and the electric three-way valve 3-2
  • the water supply port 2 is located between the indoor terminal device 205 and the electric three-way valve 3-2.
  • the controller is configured to perform water pump emptying control before performing the water pump characteristic test and pipeline characteristic test.
  • the heat pump indoor unit 10 can realize automatic emptying of the water pump self-circulation pipeline and automatic testing of the characteristics of the water pump through the self-circulation of the water pump, and automatic emptying of the full circulation pipeline of the entire water system and automatic testing of the pipeline characteristics through the full circulation of the water system.
  • the heat pump outdoor unit 1 obtains heat from outdoor air or other media, and after the refrigerant is compressed by the compressor, the refrigerant enters the terminal heat exchange component 16 of the heat pump indoor unit 10, and conducts heat exchange with the terminal heat exchange part 17. heat exchange to heat the water in the terminal heat exchange part 17 .
  • the pipeline (6) communicates with the pipeline (7).
  • the pipeline (4) is communicated with the pipeline (5).
  • the electric regulating valve 5 is completely closed, and the water pump 402 is running.
  • the electronic expansion valve 2 is controlled and adjusted according to the control rules of the heat pump system.
  • the refrigerant flows through the refrigerant gas pipe, pipeline (1), pipeline (2) and pipeline (3) of the heat pump outdoor unit 1 to the heat pump outdoor unit 1
  • the refrigerant liquid pipe forms a refrigerant circulation loop.
  • Water flows through the pipeline (4), the pipeline (5), the pipeline (6), the pipeline (7), the pipeline (8) and the pipeline (4), forming a circulation loop of the water system.
  • the heat of the heat pump indoor unit 10 is transferred to the liquid refrigerant through the water system.
  • the liquid refrigerant passes through the refrigerant pipeline, and after the pressure is increased by the compressor, the heat is released to the outdoor air.
  • the pipeline (6) communicates with the pipeline (7).
  • the pipeline (4) is communicated with the pipeline (5).
  • the electric regulating valve 5 is completely closed, and the water pump 402 is running.
  • the electronic expansion valve 2 is controlled and adjusted according to the control rules of the heat pump system.
  • the refrigerant flows through the refrigerant liquid pipe of the heat pump outdoor unit 1, the pipeline (3), the pipeline (2), the pipeline (1) and the heat pump outdoor unit 1.
  • the refrigerant air pipe forms a refrigerant circulation loop.
  • Water flows through the pipeline (4), the pipeline (5), the pipeline (6), the pipeline (7), the pipeline (8) and the pipeline (4), forming a circulation loop of the water system.
  • This mode is suitable for the water resistance calibration of the heat pump unit during installation and commissioning.
  • the heat pump system can only be activated in this mode if the cooling/heating mode is switched off.
  • the pipeline (6) communicates with the pipeline (9) by controlling the internal valve core of the electric three-way valve 3-1.
  • the pipeline (10) is communicated with the pipeline (5).
  • the electric control valve 5 is adjusted according to the set opening difference.
  • the water pump 402 operates.
  • Electronic expansion valve 2 is fully closed.
  • the controller is used to replenish water through the water supply port 1 when the pressure P1 downstream of the water pump is lower than the lower limit value M of the water system pressure after the self-circulation system of the water pump is started; the pressure P1 downstream of the water pump is higher than the lower limit value M of the water system pressure , control the water pump 402 to run intermittently until the pressure P1 downstream of the water pump 402 is between the lower limit value M and the upper limit value N of the water system pressure, and the difference between the downstream pressure of the water pump 402 at the first moment and the downstream pressure at the second moment is The absolute values of are lower than the water pressure fluctuation limit value K within the third preset time period.
  • the first moment and the second moment may be any moment, for example, when the first moment is the nth moment, the second moment may be a moment before the first moment, such as the n-1th moment.
  • the third preset duration may be any duration, for example, the third preset duration may be t5.
  • the water supply port 1 can not be closed until the automatic emptying is completed.
  • the controller controls the water pump 402 to run intermittently, the rotational speed of the water pump 402 is different between two adjacent runs.
  • the water pump 402 can run at a maximum speed, or at any speed lower than the maximum speed.
  • the water pump 402 can run at the highest speed *A, where A is a value greater than 0 and less than 1.
  • the water pump emptying control method of the heat pump unit before the water pump characteristic test includes S1 to S11.
  • the water pump starts in self-circulation.
  • step S2 P1>M, if yes, go to step S4, otherwise, go to step S3.
  • step S3 the water replenishment port 1 replenishes water, and enters step S2.
  • the water pump 402 runs at the highest speed. t1 time elapses.
  • the water pump 402 stops running. t2 time elapses.
  • the water pump 402 runs at the highest speed *A. t3 time elapses.
  • the water pump 402 runs at the highest speed.
  • step S9 M ⁇ P1 ⁇ N, if yes, go to step S10, otherwise, go to step S4.
  • step S10
  • P1 pressure detected by water pressure sensor 8-1, MPa;
  • P2 Pressure detected by water pressure sensor 8-2, MPa;
  • M lower limit of water system pressure, MPa
  • N upper limit of water system pressure, MPa
  • P1(n) water pressure at time n, MPa;
  • P1(n-1) Water pressure at time n-1, MPa;
  • t1-t5 duration, s.
  • a pump characteristic test can be performed.
  • the controller conducts a water pump characteristic test through the water pump self-circulation pipeline, including: first, controlling the conduction of the water pump self-circulation pipeline, controlling the water pump to run at the first speed, and controlling the electric regulating valve 5 to maintain the first speed within the first preset time period The corresponding first opening degree; then, calculate the average value of the downstream pressure and the upstream pressure difference of the pressure detection device within the first preset time period to obtain the first operating parameter, the first operating parameter corresponds to the head of the water pump, and the first operating parameter includes The first rotation speed and the first opening degree; secondly, calculate the average value of the flow rate detected by the flow detection device within the first preset time period, and obtain the average flow rate of the water pump corresponding to the first operating parameter; finally, according to the plurality of operating parameters The head of the corresponding water pump and the average flow rate of the water pump corresponding to the multiple operating parameters are used to obtain the test results of the water pump characteristic test.
  • the plurality of operating parameters include the first operating parameter, and the test results of the characteristic test
  • the first rotational speed of the water pump 402 can be multiple, and each rotational speed can correspond to multiple openings of the electric regulating valve 5 , and the water pump 402 needs to maintain a set duration at each opening corresponding to each rotational speed.
  • the first preset duration may be any duration, for example, the first preset duration may be t11 time.
  • the water pump 402 runs at the highest speed.
  • Procedure 1 Fully close the electric regulating valve 5, and then open the valve (opening degree 20%). After the time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to the coordinate points of the 20% opening of the electric regulating valve 5 shown in FIG. 24 .
  • Procedure 2 The electric control valve 5 is opened (the opening degree is 50%). After the time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to the coordinate points of the 50% opening of the electric regulating valve 5 shown in FIG. 24 .
  • Procedure 3 The electric control valve 5 is opened (the opening degree is 70%). After the time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to the coordinate points of the 70% opening of the electric regulating valve 5 shown in FIG. 24 .
  • Procedure 4 The electric control valve 5 is opened (the opening degree is 100%). After the time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to the coordinate points at which the opening degree of the electric regulating valve 5 shown in FIG. 24 is 100%.
  • the water pump 402 runs at the highest speed*75%.
  • repeating S3 to S7 can obtain the water pump characteristic curve corresponding to the maximum speed*75% of the water pump 402.
  • the water pump 402 runs at the highest speed*50%. If the lower limit speed of the set water pump is reached, the test will end after the operation is completed.
  • repeating S3 to S7 can obtain the water pump characteristic curve corresponding to the maximum speed*50% of the water pump 402.
  • the water pump 402 operates at a maximum speed of 25%, as shown in the curve of the water pump 402 maximum speed x 25% as shown in FIG. 24 . If the lower limit speed of the set water pump is reached, the test will end after the operation is completed.
  • repeating S3 to S7 can obtain the water pump characteristic curve corresponding to the maximum speed*25% of the water pump 402.
  • the lower limit speed of the water pump 402, as shown in FIG. 24 is the curve of the lower limit speed of the water pump 402.
  • repeating S3 to S7 can obtain the water pump characteristic curve corresponding to the lower limit speed of the water pump 402 .
  • ⁇ P head of the water pump
  • ⁇ P is the average pressure difference (P1-P2) before and after the water pump within t11, MPa;
  • Water pressure sensor 8-1 is detecting pressure, MPa;
  • P2 Pressure detected by water pressure sensor 8-2, MPa;
  • t11 the duration of the fixed opening of the electric control valve 5, s.
  • the heat pump system automatically draws the characteristic curve of the water pump through the automatic test data of the characteristic of the water pump.
  • This curve is embedded in the internal program of the heat pump system, and can also be displayed on the user-end controller interface, which is convenient for installation and maintenance personnel to check the waterway.
  • This mode is suitable for the water resistance calibration of the heat pump unit during installation and commissioning.
  • the heat pump system can only activate this mode if the cooling/heating mode is switched off.
  • the pipeline (6) communicates with the pipeline (7) by controlling the internal spool of the electric three-way valve 3-1.
  • the pipeline (4) is communicated with the pipeline (5).
  • the electric regulating valve 5 is completely closed.
  • the water pump 402 operates.
  • Electronic expansion valve 2 is fully closed.
  • the refrigerant circulation loop is closed.
  • the water in some system pipelines in the heat pump system flows through pipelines (5), pipelines (6), pipelines (7), pipelines (8), pipelines (4) and pipelines (5), forming a water system circulation loop .
  • the controller is used to replenish water through the water supply port 2 when the downstream pressure P1 of the water pump is lower than the lower limit value M of the water system pressure after the full cycle of the water system is started; when the downstream pressure P1 of the water pump is higher than the lower limit value M of the water system pressure , control the water pump 402 to run intermittently until the downstream pressure P1 of the water, 402 is between the lower limit value M and the upper limit value N of the water system pressure, and the downstream pressure of the water pump 402 at the first moment is equal to the downstream pressure at the second moment.
  • the absolute values of the differences are all lower than the water pressure fluctuation limit value K within the third preset time period.
  • first moment and the second moment may be any moment, for example, when the first moment is the nth moment, the second moment may be a moment before the first moment, such as (n-1) moment.
  • the third preset duration may be any duration, for example, the third preset duration may be t5.
  • the water replenishment port 2 cannot be closed until the automatic emptying is completed.
  • the controller controls the water pump 402 to run intermittently, the rotational speed of the water pump 402 is different between two adjacent runs.
  • the water pump 402 can run at a maximum speed, or at any speed lower than the maximum speed.
  • the water pump 402 can run at the highest speed *A, where A is a value greater than 0 and less than 1.
  • the water pump emptying control method of the heat pump unit before the pipeline characteristic test is:
  • step S2 P1>M, if yes, go to step S4, otherwise, go to step S3.
  • step S3 the water replenishment port 2 replenishes water, and enters step S2.
  • the water pump 402 runs at the highest speed. t6 time elapses.
  • the water pump 402 stops running. t7 time elapses.
  • the water pump 402 runs at the highest speed *A. t8 time elapses.
  • the water pump 402 runs at the highest speed.
  • step S9 M ⁇ P1 ⁇ N, if yes, go to step S10, otherwise, go to step S4.
  • step S10
  • P1 pressure detected by water pressure sensor 8-1, MPa;
  • P2 Pressure detected by water pressure sensor 8-2, MPa;
  • M lower limit of water system pressure, MPa
  • N upper limit of water system pressure, MPa
  • P1(n) water pressure at time n, MPa;
  • P1(n-1) Water pressure at time n-1, MPa;
  • t6-t10 duration, s.
  • the controller conducts a pipeline characteristic test through the full circulation pipeline of the water system, including: first, controlling the full circulation management of the water system to conduct, controlling the water pump to run at the second speed for the second preset time; then, calculating the second preset time The average value of the downstream pressure of the internal pressure detection device and the upper pressure difference is obtained to obtain the internal resistance of the pipeline corresponding to the second rotational speed; then, the average value of the flow detected by the flow detection device within the second preset time period is calculated to obtain the second rotational speed The corresponding flow average value; finally, according to the pipeline internal resistance corresponding to multiple rotational speeds and the flow average value corresponding to multiple rotational speeds, the test result of the pipeline characteristic test is obtained; the test result of the pipeline characteristic test includes the pipeline characteristic curve.
  • the second rotational speed of the water pump 402 can be multiple, and each rotational speed needs to be maintained for a set time length, and the average value ⁇ P' of the downstream pressure and the upstream pressure difference detected by the pressure detection device within the set time length is calculated, and ⁇ P' is The internal resistance of the pipeline; at the same time, calculate the average value Q' of the flow detected by the flow detection device within the set time period.
  • the second preset duration may be any duration, for example, the second preset duration may be t12.
  • the water pump 402 runs at the highest speed. After the time t12 elapses, ⁇ P' and Q' are calculated. These ⁇ P' and Q' correspond to the coordinate points of the highest rotational speed of the water pump 402 shown in FIG. 27 .
  • the water pump 402 runs at the highest speed*75%. After the time t12 elapses, ⁇ P' and Q' are calculated, and the ⁇ P' and Q' correspond to the coordinate point of the maximum rotational speed*75% of the water pump 402 shown in FIG. 27 .
  • the water pump 402 runs at the highest speed*50%. After the time t12 elapses, ⁇ P' and Q' are calculated, and the ⁇ P' and Q' correspond to the coordinate point of the maximum rotational speed of the water pump 402*50% shown in FIG. 27 .
  • the water pump 402 runs at the highest speed*25%. After the time t12 elapses, ⁇ P' and Q' are calculated, and the ⁇ P' and Q' correspond to the coordinate point of the maximum rotational speed of the water pump 402*25% shown in FIG. 27 .
  • ⁇ P' pipeline internal resistance
  • ⁇ P' is the average value of the pressure difference (P1-P2) before and after the water pump 402 within t12, MPa;
  • Water pressure sensor 8-1 is detecting pressure, MPa;
  • P2 Pressure detected by water pressure sensor 8-2, MPa;
  • t12 continuous running time of the water pump 402 at a fixed speed, s.
  • the heat pump system can automatically draw a pipeline characteristic curve based on the pipeline characteristic automatic test data. This curve is embedded in the internal program of the heat pump system, and can also be displayed on the user-end controller interface, which is convenient for installation and maintenance personnel to check the waterway.
  • the heat pump system can define three different water pump control functions: constant speed, constant water volume and constant water temperature difference in heating mode and cooling mode.
  • This function is suitable for situations where the heat pump system is normally operated in cooling/heating mode.
  • the heat pump system can only activate this function when the cooling/heating mode is turned on. Under this function, the water pump 402 will run according to the set speed.
  • the pipeline (6) communicates with the pipeline (7).
  • the pipeline (4) is communicated with the pipeline (5).
  • the electric regulating valve 5 is completely closed.
  • the water pump 402 operates at a set speed.
  • the electronic expansion valve 2 is controlled and adjusted according to the control rules of the heat pump system.
  • the constant speed control method is:
  • the user sets the rotational speed on the operation interface.
  • the default maximum speed if the user does not actively set it, it will be executed according to the maximum speed.
  • the water pump 402 runs according to the set speed.
  • the cooling/heating mode is turned off. t13 time elapsed, t13: water pump delay stop time, s.
  • This function is suitable for situations where the heat pump system is normally operated in cooling/heating mode. This function can only be activated when the cooling/heating mode of the heat pump system is turned on.
  • the pipeline (6) communicates with the pipeline (7).
  • the pipeline (4) is communicated with the pipeline (5).
  • the electric regulating valve 5 is completely closed.
  • the water pump 402 operates.
  • the electronic expansion valve 2 is controlled and adjusted according to the control rules of the heat pump system.
  • the heat pump system will form a pump-pipe characteristic curve based on the water pump characteristic curve measured in the water pump self-circulation mode (Figure 24) and the pipeline characteristic curve measured in the water system full circulation mode (Figure 27), as shown in Figure 29.
  • the controller is further configured to: firstly, obtain the first water flow rate; then obtain the rotational speed corresponding to the first water flow rate according to the first water flow rate and the pipeline characteristic curve; finally, control the water pump to run at the rotational speed corresponding to the first water flow rate.
  • the first water flow rate is the demanded water flow rate, for example, the required water flow rate set by the user, and the operating point corresponding to the pipeline characteristic curve is obtained according to the required water flow rate, and the water pump speed corresponding to the water pump characteristic curve passing through the operating point is selected as The target speed of the pump controls the pump operation.
  • the heat pump system first obtains the corresponding operating point (such as operating point 1) on the pipeline characteristics through the water flow rate, and selects The speed curve of the water pump (maximum speed of water pump 4 ⁇ 25%), the speed of water pump corresponding to this curve (maximum speed of water pump 4 ⁇ 25%) can be used as the determined running speed of the water pump.
  • the controller when the operating point is not on the measured characteristic curve of the water pump, can also perform linear interpolation on adjacent characteristic curves of the water pump to obtain the target rotational speed of the water pump.
  • the heat pump system first obtains the corresponding operating point (such as operating point 2) on the pipeline characteristics through the water flow rate, which has not been measured
  • the appropriate water pump speed is finally obtained by performing linear interpolation on the adjacent water pump characteristic curve (maximum speed of water pump 4 ⁇ 25% and lower limit speed of water pump 4).
  • the speed of the water pump is dynamically adjusted during operation according to the real-time data measured by the water flow meter 9, as shown in Figure 30:
  • the water pump 402 operates at a constant flow speed. t14 time elapsed.
  • R (n) the water pump rotational speed ratio (with the ratio of maximum rotational speed, %) at n moment;
  • R(n-1) water pump speed ratio at time n-1 (ratio to maximum speed, %);
  • ⁇ R(n) change ratio of pump speed at time n (constant water flow control), %;
  • ⁇ R1(n) The change ratio of the speed of the pump under PID control at time n (constant water flow control), %;
  • ⁇ R2(n) change ratio of pump speed for overshoot and undershoot control at time n (constant water flow control), %;
  • ⁇ 1, ⁇ 2 the PID control constant ( ⁇ 0) of fixed water flow control
  • ⁇ 3 the control constant of the overshoot and undershoot of constant water flow control
  • Qs(n) set water flow rate at time n, unit m 3 /h;
  • t14 The running time of the water pump at a constant water volume speed, s.
  • This function is suitable for situations where the heat pump system is normally operated in cooling/heating mode.
  • the heat pump system can only start this mode when the cooling/heating mode is turned on.
  • the pipeline (6) communicates with the pipeline (7).
  • the pipeline (4) is communicated with the pipeline (5).
  • the electric regulating valve 5 is completely closed.
  • the water pump 402 operates.
  • the electronic expansion valve 2 is controlled and adjusted according to the control rules of the air source heat pump.
  • the controller is also configured to: firstly, obtain the water temperature difference required by the user; then, obtain the current water temperature difference according to the current outlet water temperature and return water temperature of the terminal heat exchange unit; then, obtain the current water temperature difference according to the current water temperature difference and the flow rate detection device detected
  • the difference between the current water flow rate and the water temperature required by the user is used to calculate the target water flow rate; finally, the water pump is controlled to run at the preset maximum speed. After the operation is stable, the water pump is controlled to run at the target speed corresponding to the target water flow rate.
  • the target water flow includes the required water flow, which is determined by the current water temperature difference and the current water flow.
  • the operation of the water pump 402 is controlled by obtaining the target rotational speed of the water pump according to the demanded water flow.
  • the water pump 402 In the initial stage of operation of the heat pump system, the water pump 402 will operate at the set maximum speed.
  • the speed of the water pump is dynamically adjusted during operation according to the temperature values detected by the outlet water temperature sensor 501 and the return water temperature sensor 502, as shown in Figure 31:
  • the water pump 402 operates at a constant temperature difference and rotating speed. t15 time elapsed.
  • ⁇ R3(n) ⁇ 4* ⁇ tr(n)- ⁇ tr(n-1) ⁇ + ⁇ 5* ⁇ tr(n).
  • ⁇ R4(n) ⁇ 6* ⁇ tr(n).
  • R (n) the water pump rotational speed ratio (with the ratio of maximum rotational speed, %) at n moment;
  • R(n-1) water pump speed ratio at time n-1 (ratio to maximum speed, %);
  • ⁇ R'(n) change ratio of pump speed at time n (constant water temperature difference control), %;
  • ⁇ R3(n) The change ratio of pump speed controlled by PID at time n (constant water temperature difference control), %;
  • ⁇ R4(n) change ratio of water pump speed for overshoot and undershoot control at time n (constant water temperature difference control), %;
  • ⁇ 4, ⁇ 5 the PID control constant ( ⁇ 0) of fixed water temperature difference control
  • ⁇ 6 the control constant of the overshoot and undershoot of constant water temperature difference control
  • ⁇ t(n) measured water temperature difference at time n, unit °C;
  • ⁇ ts(n) The set water temperature difference at time n, unit °C;
  • t15 The running time of the pump at constant temperature difference and speed, s.
  • the heat pump system as shown in FIG. 21 can realize the water pump characteristic test and the pipeline characteristic test, and realize the automatic adjustment of the speed of the water pump according to the test results without repeated debugging. At the same time, constant speed, constant flow, and constant temperature difference control of the heat pump system can also be realized according to user needs.
  • Some embodiments of the present disclosure provide a method for controlling a heat pump system, where the heat pump system may be the heat pump system described in any of the foregoing embodiments.
  • the control method of the heat pump system includes: Step 321 to Step 324 .
  • Step 321 determine whether the heat pump system satisfies a preset condition, and the preset condition includes a low-temperature heating condition, a defrosting condition, a high-temperature heating condition or a rapid heating condition.
  • Step 322 if the heat pump system meets the low-temperature heating condition or the defrosting condition, control the terminal heat exchange unit to perform heat exchange with the third heat exchange unit.
  • Low-temperature heating conditions include but are not limited to the set temperature being lower than the first preset temperature; defrosting conditions include but are not limited to the temperature of the terminal heat exchange part 17 being higher than the second preset temperature, and the second preset temperature can be, for example, 8 °C.
  • the first compressor 33 when the heat pump system meets the low-temperature heating condition or the defrosting condition, the first compressor 33 is controlled to stop; or, the first compressor 33 is controlled to stop, and the first valve element 22 and the second valve element are simultaneously controlled 23 is closed, and the third valve element 24 is controlled to communicate.
  • Step 323 if the heat pump system meets the high-temperature heating condition, control the terminal heat exchange part to perform heat exchange with the fourth heat exchange part.
  • the high temperature heating condition includes that the set temperature is higher than the third preset temperature.
  • Step 324 If the heat pump system meets the rapid heating condition, control the terminal heat exchange unit to perform heat exchange with the third heat exchange unit and the fourth heat exchange unit.
  • the rapid heating condition includes that the heat pump system needs to be heated to the fourth preset temperature within a short time. For example, when the water heater is turned on and the set temperature is 40°C, the heat pump system needs to heat up to 40°C in a short time.
  • the first compressor 33 When the heat pump system meets the fast heating condition, the first compressor 33 is controlled to run; or, the first compressor 33 is controlled to run while the first valve element 22 , the second valve element 23 and the third valve element 24 are controlled to communicate.
  • the control method of the heat pump system when the heat pump system satisfies the low-temperature heating condition, the heat exchange part of the control terminal performs heat exchange with the third heat exchange part. stop running.
  • the control method of the heat pump system provided by the embodiment of the present disclosure can prevent the high-temperature stage circulation system from failing due to failure of the high-temperature stage circulation system.
  • the problem of generating a sufficient pressure difference to cause low reliability of system operation ensures reliable operation of the heat pump system. That is to say, the heat pump system control method provided by the embodiments of the present disclosure can independently control whether the low-temperature stage circulation system and the high-temperature stage circulation system are running, with high flexibility and low energy consumption.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Sustainable Development (AREA)
  • Health & Medical Sciences (AREA)
  • Biomedical Technology (AREA)
  • Computer Hardware Design (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

La présente invention concerne un système de pompe à chaleur, qui comprend au moins une unité intérieure de pompe à chaleur. L'unité intérieure de pompe à chaleur comprend un échangeur de chaleur en cascade (11) et un ensemble échangeur de chaleur terminal (16). L'échangeur de chaleur en cascade (11) comprend une première partie d'échange de chaleur (12) et une deuxième partie d'échange de chaleur (14), la première partie d'échange de chaleur (12) étant raccordée à une conduite de circulation à étage basse température (13), et un premier fluide frigorigène étant présent dans la conduite de circulation à étage basse température (13) ; et la deuxième partie d'échange de chaleur (14) est raccordée à une conduite de circulation à étage haute température (15), il y a un second fluide frigorigène dans la conduite de circulation à étage haute température (15), et la deuxième partie d'échange de chaleur (14) est conçue pour échanger de la chaleur avec la première partie d'échange de chaleur (12). L'ensemble échangeur de chaleur terminal (16) comprend une troisième partie d'échange de chaleur (18), une quatrième partie d'échange de chaleur (19) et une partie d'échange de chaleur terminale (17), la troisième partie d'échange de chaleur (18) étant raccordée à la conduite de circulation à étage basse température (13) ; la quatrième partie d'échange de chaleur (19) est raccordée à la conduite de circulation à étage haute température (15) ; et la partie d'échange de chaleur terminale (17) est raccordée à un appareil d'extrémité intérieur, et est conçue pour échanger de la chaleur avec la troisième partie d'échange de chaleur (18), ou échanger de la chaleur avec la quatrième partie d'échange de chaleur (19), ou échanger de la chaleur avec la troisième partie d'échange de chaleur (18) et la quatrième partie d'échange de chaleur (19).
PCT/CN2022/097721 2021-06-08 2022-06-08 Système de pompe à chaleur et procédé de commande associé WO2022257993A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202280008879.7A CN116670436A (zh) 2021-06-08 2022-06-08 热泵系统及其控制方法
EP22819590.5A EP4354048A1 (fr) 2021-06-08 2022-06-08 Système de pompe à chaleur et procédé de commande associé

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
CN202110639064.6 2021-06-08
CN202110639064.6A CN113531935A (zh) 2021-06-08 2021-06-08 一种复叠热泵循环系统和控制方法
CN202110709626.X 2021-06-25
CN202110709626.XA CN113432172A (zh) 2021-06-25 2021-06-25 热泵机组室内单元和热泵机组
CN202123050748.7 2021-12-07
CN202123050748.7U CN216521915U (zh) 2021-12-07 2021-12-07 空气源热泵系统
CN202210374161.1A CN114659294B (zh) 2022-04-11 2022-04-11 一种空气源热泵
CN202210374161.1 2022-04-11

Publications (1)

Publication Number Publication Date
WO2022257993A1 true WO2022257993A1 (fr) 2022-12-15

Family

ID=84424780

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/097721 WO2022257993A1 (fr) 2021-06-08 2022-06-08 Système de pompe à chaleur et procédé de commande associé

Country Status (2)

Country Link
EP (1) EP4354048A1 (fr)
WO (1) WO2022257993A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108050630A (zh) * 2018-01-23 2018-05-18 厦门鑫中锐能源科技有限公司 进出水咀位置可调的空调热泵系统
CN116294266A (zh) * 2023-02-27 2023-06-23 清华大学 可实现单级运行和复叠运行的空气源热泵系统

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110120179A1 (en) * 2009-11-20 2011-05-26 Sim Won Chin Heat pump type cooling/heating apparatus
CN102269444A (zh) * 2011-05-27 2011-12-07 哈尔滨工业大学 一种供热与供冷水循环的能量控制系统与控制方法
CN103076080A (zh) * 2013-01-06 2013-05-01 大连理工大学 基于局部压力测量二维流路内t-s波的方法
CN103090483A (zh) * 2013-01-23 2013-05-08 青岛奥利凯中央空调有限公司 自测调控换热量的水源热泵空调及其方法
CN104848598A (zh) * 2015-05-27 2015-08-19 广东欧科空调制冷有限公司 宽进水温度水源热泵系统
CN108072173A (zh) * 2018-01-23 2018-05-25 浙江正理生能科技有限公司 一种复叠式制冷除霜热水器
CN108759144A (zh) * 2018-07-21 2018-11-06 青岛奥利凯中央空调有限公司 一种复叠式超低温空气源热泵机组及其控制方法
CN113432172A (zh) * 2021-06-25 2021-09-24 青岛海信日立空调系统有限公司 热泵机组室内单元和热泵机组
CN216521915U (zh) * 2021-12-07 2022-05-13 青岛海信日立空调系统有限公司 空气源热泵系统

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110120179A1 (en) * 2009-11-20 2011-05-26 Sim Won Chin Heat pump type cooling/heating apparatus
CN102269444A (zh) * 2011-05-27 2011-12-07 哈尔滨工业大学 一种供热与供冷水循环的能量控制系统与控制方法
CN103076080A (zh) * 2013-01-06 2013-05-01 大连理工大学 基于局部压力测量二维流路内t-s波的方法
CN103090483A (zh) * 2013-01-23 2013-05-08 青岛奥利凯中央空调有限公司 自测调控换热量的水源热泵空调及其方法
CN104848598A (zh) * 2015-05-27 2015-08-19 广东欧科空调制冷有限公司 宽进水温度水源热泵系统
CN108072173A (zh) * 2018-01-23 2018-05-25 浙江正理生能科技有限公司 一种复叠式制冷除霜热水器
CN108759144A (zh) * 2018-07-21 2018-11-06 青岛奥利凯中央空调有限公司 一种复叠式超低温空气源热泵机组及其控制方法
CN113432172A (zh) * 2021-06-25 2021-09-24 青岛海信日立空调系统有限公司 热泵机组室内单元和热泵机组
CN216521915U (zh) * 2021-12-07 2022-05-13 青岛海信日立空调系统有限公司 空气源热泵系统

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108050630A (zh) * 2018-01-23 2018-05-18 厦门鑫中锐能源科技有限公司 进出水咀位置可调的空调热泵系统
CN108050630B (zh) * 2018-01-23 2023-09-19 厦门鑫中锐能源科技有限公司 进出水咀位置可调的空调热泵系统
CN116294266A (zh) * 2023-02-27 2023-06-23 清华大学 可实现单级运行和复叠运行的空气源热泵系统
CN116294266B (zh) * 2023-02-27 2024-04-19 清华大学 可实现单级运行和复叠运行的空气源热泵系统

Also Published As

Publication number Publication date
EP4354048A1 (fr) 2024-04-17

Similar Documents

Publication Publication Date Title
WO2022257993A1 (fr) Système de pompe à chaleur et procédé de commande associé
EP2789933B1 (fr) Système de chauffage de type pompe à chaleur/d'alimentation en eau chaude
CN106642416B (zh) 空调系统、复合冷凝器、空调系统的运行控制方法及装置
US20180017271A1 (en) Multi-online system
CN106322768B (zh) 热水器及其控制方法
CN109556210B (zh) 一种低温型三联供热泵系统的控制方法
CN110260416B (zh) 分区换热器组件、空调器及分区换热器组件的控制方法
WO2018076934A1 (fr) Climatiseur et système de réfrigération associé
CN207515270U (zh) 一种热泵系统
CN103842736A (zh) 制冷装置
JPH04124544A (ja) 空気調和機
CN114279101A (zh) 四管制系统、控制方法、装置及空调
CN1982798A (zh) 一种压缩机补气系统及补气控制方法
CN107906811B (zh) 热泵机组防冷冻控制方法
CN111649445B (zh) 一种用于空调的制冷剂调节系统及空调
KR101456878B1 (ko) 히트펌프 성능평가 시스템의 제어방법
CN101498521A (zh) 一种空气源三用热泵热水机
CN203869367U (zh) 一种地暖、热水器、空调三合一机组
CN213983785U (zh) 一种三管制直流变频恒温恒湿空调机组
CN105650872A (zh) 一种热水器
CN116670436A (zh) 热泵系统及其控制方法
CN2886422Y (zh) 一种工作稳定的快速直出热水的热泵热水机
CN113357691A (zh) 一种空调、地暖、热水三合一低温空气源热泵机组
CN113432172A (zh) 热泵机组室内单元和热泵机组
CN112161350A (zh) 换热速率可调的空调机组及其控制方法

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22819590

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 202280008879.7

Country of ref document: CN

WWE Wipo information: entry into national phase

Ref document number: 2022819590

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2022819590

Country of ref document: EP

Effective date: 20240108