EP4354048A1 - Système de pompe à chaleur et procédé de commande associé - Google Patents

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

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Publication number
EP4354048A1
EP4354048A1 EP22819590.5A EP22819590A EP4354048A1 EP 4354048 A1 EP4354048 A1 EP 4354048A1 EP 22819590 A EP22819590 A EP 22819590A EP 4354048 A1 EP4354048 A1 EP 4354048A1
Authority
EP
European Patent Office
Prior art keywords
water
heat exchange
exchange portion
heat
temperature
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22819590.5A
Other languages
German (de)
English (en)
Inventor
Dongzhe LI
Yuanpeng WANG
Jixue ZUO
Xingxiang XIA
Weixing Chen
Cuilian PAN
Qinghang GUAN
Shoushan LI
Qingbo Wang
Hua Fu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Original Assignee
Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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 Qingdao Hisense Hitachi Air Conditioning System Co Ltd filed Critical Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Publication of EP4354048A1 publication Critical patent/EP4354048A1/fr
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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 field of heat pump technologies, and in particular, to a heat pump system and a control method of a heat pump system.
  • Heat pump systems uses electric energy as a driving power and uses outdoor ambient air as a heat source to provide heat to the adjusted object. Compared with electric water heaters and gas water heaters, the heat pump systems have characteristics of high energy efficiency and low energy consumption, so that the heat pump systems have received widespread attention in the industry.
  • some embodiments of the present disclosure provide a heat pump system.
  • the heat pump system includes at least one heat pump indoor unit.
  • the heat pump indoor unit includes a cascade heat exchanger and a terminal heat exchanger assembly.
  • the cascade heat exchanger includes: a first heat exchange portion and a second heat exchange portion.
  • the first heat exchange portion 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 portion is connected to a high-temperature-stage circulation pipeline, and there is a second refrigerant in the high-temperature-stage circulation pipeline, and the second heat exchange portion is configured to perform heat exchange with the first heat exchange portion.
  • the terminal heat exchanger assembly includes: a third heat exchange portion, a fourth heat exchange portion, and a terminal heat exchange portion.
  • the third heat exchange portion is connected to the low-temperature-stage circulation pipeline.
  • the fourth heat exchange portion is connected to the high-temperature-stage circulation pipeline.
  • the terminal heat exchange portion is connected to an indoor end apparatus, and the terminal heat exchange portion is configured to perform heat exchange with the third heat exchange portion, or the fourth heat exchange portion, or the third heat exchange portion and the fourth heat exchange portion.
  • some embodiments of the present disclosure further provide a control method of the above heat pump system.
  • the heat pump system is any heat pump system described above.
  • the control method of the heat pump system includes: determining whether the heat pump system satisfies a preset condition, and the preset condition including a low-temperature heating condition, a defrosting condition, a high-temperature heating condition or a rapid heating condition; controlling the terminal heat exchange portion to exchange heat with the third heat exchange portion if the heat pump system satisfies the low-temperature heating condition or the defrosting condition; controlling the terminal heat exchange portion to exchange heat with the fourth heat exchange portion if the heat pump system satisfies the high-temperature heating condition; controlling the terminal heat exchange portion to exchange heat with the third heat exchange portion and the fourth heat exchange portion if the heat pump system satisfies the rapid heating condition.
  • a heat pump system may use outdoor ambient air or other media as a heat source, and uses a compressor, a condenser, a throttling device, and an evaporator to perform a refrigerant cycle, so as to provide heat to an indoor end apparatus.
  • the present disclosure does not limit a type of the heat pump system, and the following embodiments are described by considering an example in which the heat pump system is an air source heat pump.
  • the air source heat pump cannot produce hot water from 55 °C to 60 °C or above due to limitation of a pressure ratio of the compressor and physical properties of the refrigerant.
  • the temperature of the water produced by the air source heat pump will also have a significant attenuation.
  • a maximum heating temperature of the air source heat pump reaches only 60 °C.
  • usage scenes such as hospitals, food, and hotels widely using high temperature water are still unable to directly produce high-temperature hot water at a temperature of 80 °C to 90 °C through traditional air source heat pump products.
  • a cascade heat pump system may be used.
  • the cascade heat pump system includes a low-temperature-stage circulation system and a high-temperature-stage circulation system.
  • the low-temperature-stage circulation system and the high-temperature-stage circulation system operate simultaneously to produce high-temperature hot water.
  • the flexibility of the cascade heat pump system is poor.
  • the cascade heat pump system In a case where a set water temperature is low, the cascade heat pump system must also start the low-temperature-stage circulation system and the high-temperature-stage circulation system simultaneously, which will cause the high-temperature-stage circulation system to fail to generate sufficient pressure difference. As a result, the pressure ratio deviates from the normal operating range, which is not conducive to the reliable operation of the high-temperature-stage 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 portion 12 is connected to a low-temperature-stage circulation pipeline 13, and there is a first refrigerant in the low-temperature-stage circulation pipeline 13.
  • the second heat exchange portion 14 is connected to a high-temperature-stage circulation pipeline 15. There is a second refrigerant in the high-temperature-stage circulation pipeline 15, and the second heat exchange portion 14 is configured to exchange heat with the first heat exchange portion 12.
  • the cascade heat exchanger 11 may also be referred to as an evaporative condenser.
  • the first heat exchange portion 12 and the second heat exchange portion 14 in the cascade heat exchanger 11 have different functions.
  • the first refrigerant in the first heat exchange portion 12 condenses and releases heat, and the second refrigerant in the second heat exchange portion 14 absorbs the heat released by the first refrigerant in the first heat exchange portion 12; in a case where the heat pump system is cooling, the first refrigerant in the first heat exchange portion 12 evaporates and absorbs heat, and the second refrigerant in the second heat exchange portion 14 exchanges heat with the first refrigerant in the first heat exchange portion 12.
  • first refrigerant and the second refrigerant may be same or different.
  • first refrigerant and the second refrigerant each may be any one of refrigerants such as R410A, R134a, R12, R22, R32, R290, or R744.
  • the following embodiments are described by considering an example in which the first refrigerant is R41 0A and the second refrigerant is R134a.
  • the terminal heat exchanger assembly 16 includes a terminal heat exchange portion 17, a third heat exchange portion 18, and a fourth heat exchange portion 19.
  • the third heat exchange portion 18 is connected to the low-temperature-stage circulation pipeline 13
  • the fourth heat exchange portion 19 is connected to the high-temperature-stage circulation pipeline 15
  • the terminal heat exchange portion 17 is connected to the indoor end apparatus.
  • the terminal heat exchange portion 17 includes a medium to be heated, and the medium to be heated is mainly water.
  • the indoor end apparatus may be a water terminal, such as a floor heating, a radiator or a water heater.
  • the terminal heat exchange portion 17 is configured to perform heat exchange with the third heat exchange portion 18, or perform heat exchange with the fourth heat exchange portion 19, or perform heat exchange with the third heat exchange portion 18 and the fourth heat exchange portion 19.
  • operating modes of the heat pump system include but are not limited to the heating mode and the cooling mode.
  • the heating mode includes but is not limited to a low-temperature heating mode, a high-temperature heating mode and a rapid heating mode.
  • the cooling mode includes but is not limited to a defrosting mode.
  • the heat pump system satisfies a low-temperature heating condition
  • the heat pump system operates in the low-temperature heating mode.
  • the low-temperature heating condition includes but is not limited to that a set temperature (e.g., a water temperature required by a user) is lower than a first preset temperature, and the low-temperature heating mode may produce medium-temperature water.
  • the heat pump system In a case where the heat pump system satisfies a high-temperature heating condition, the heat pump system operates in the high-temperature heating mode; the high-temperature heating condition includes but is not limited to that a set temperature is higher than a third preset temperature, and the high-temperature heating mode may produce high-temperature water.
  • the heat pump system In a case where the heat pump system satisfies a defrosting condition, the heat pump system operates in the defrosting mode; the defrosting condition includes but is not limited to that a temperature of the terminal heat exchange portion 17 is higher than a second preset temperature.
  • the heat pump system In a case where the heat pump system satisfies a rapid heating condition, the heat pump system operates in the rapid heating mode, and the rapid heating mode may also produce high-temperature water.
  • the rapid heating mode means that the heat pump system needs to be heated up to a fourth preset temperature in short time.
  • the indoor end apparatus is a water heater
  • the heat pump system needs to complete heating in short time, so that the heat pump system enters the rapid heating mode.
  • the operating modes of the heat pump system are related to instructions sent by the user, and parameters such as a water inlet temperature of the terminal heat exchange portion 17. For example, if an instruction for entering the rapid heating mode sent by the user is received and a water inlet temperature of a water circulation flow path is low, the heat pump system enters the rapid heating mode. For another example, if an instruction for defrosting sent by the user is received, the heat pump system enters the defrosting mode.
  • the term “lower” includes less than or equal to, and the term “higher” includes greater than or equal to.
  • the first preset temperature may be less than or equal to the third preset temperature.
  • the embodiments of the present disclosure do not limit values of the first preset temperature, the second preset temperature, the third preset temperature, and the fourth preset temperature.
  • the heat pump system operates in the low-temperature heating mode
  • the low-temperature-stage circulation system operates, and the terminal heat exchange portion 17 exchanges heat with the third heat exchange portion 18.
  • the high-temperature-stage circulation system operates, and the terminal heat exchange portion 17 exchanges heat with the fourth heat exchange portion 19.
  • the terminal heat exchange portion 17 performs heat exchange with the third heat exchange portion 18 and the fourth heat exchange portion 19 simultaneously, so as to reach a temperature set by the user in short time.
  • the low-temperature-stage circulation system operates, and the terminal heat exchange portion 17 exchanges heat with the third heat exchange portion 18.
  • the difference between the operation of the heat pump system in the defrosting mode and the operation of the heat pump system in the low-temperature heating mode is that a 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 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 the high-temperature-stage circulation system and the 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.
  • the outdoor heat exchanger 32, the second compressor 30 and the four-way valve 31 are connected with each other through the low-temperature-stage circulation pipeline 13.
  • the outdoor heat exchanger 32 includes a finned heat exchanger.
  • the second compressor 30 may also be referred to as a low-temperature-stage compressor.
  • the second compressor 30 and a first compressor 33 may be 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 the first refrigerant R410A.
  • the high-temperature-stage circulation system includes the high-temperature-stage circulation pipeline 15, and the high-temperature-stage circulation pipeline 15 has the 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.
  • a first valve element 22, a second valve element 23, and a third valve element 24 By controlling opening and closing of the first valve element 22, the second valve element 23, and the third valve element 24, it is possible for the heat pump system to control whether the high-temperature-stage circulation system operates according to actual usage requirements.
  • the first valve element 22 is disposed between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13, and the first valve element 22 is configured to adjust a flow rate of the first refrigerant entering the first heat exchange portion 12.
  • 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 adjust a flow rate of the second refrigerant entering the second heat exchange portion 14 and the fourth heat exchange portion 19.
  • 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 adjust a flow rate of the first refrigerant entering the third heat exchange portion 18.
  • valve elements e.g., the first valve element 22, the second valve element 23, and the third valve element 24
  • the valve elements are electronic expansion valves that may adjust an opening degree between a fully open position and a fully closed position.
  • Operating states of the first valve element 22, the second valve element 23, and the third valve element 24 may include, for example, an opening state, a closed state, and a throttling state.
  • the heat pump indoor unit 10 further includes a first compressor 33, and the first compressor 33 is 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 (i.e., stops operating).
  • the first valve element 22 is configured to operate in the closed state, so as to close a passage between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13.
  • the third valve element 24 is configured to operate in the open state, so as to open a passage between the third heat exchange portion 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 and evaporates, and then enters the second compressor 30 for compression, so as to obtain a high-temperature and high-pressure gaseous first refrigerant.
  • the first refrigerant enters the low-temperature-stage circulation pipeline 13 of the heat pump system. Since the first valve element 22 closes the refrigerant passage between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13, the first refrigerant cannot circulate through the first heat exchange portion 12, but enters the third heat exchange portion 18, and exchanges heat with the medium (e.g., water) in the terminal heat exchange portion 17. The first refrigerant releases heat in the third heat exchange portion 18, and heats water in the terminal heat exchange portion 17 to a set temperature, so as to achieve low-temperature-stage heating of the heat pump system.
  • the medium e.g., water
  • the first refrigerant After the first refrigerant completes heating the medium in the terminal heat exchange portion 17, the first refrigerant flows out from the third heat exchange portion 18, and then returns to the heat pump outdoor unit 1 through the third valve element 24 in the open state. Then, the first refrigerant is throttled back to a low-temperature and low-pressure state by a throttling device 29 disposed in the heat pump outdoor unit 1. In a case where the heat pump system operates in the low-temperature heating mode, a flow path of the first refrigerant is shown as F1 in FIG. 3 .
  • the outdoor heat exchanger 32 is used as an evaporator. In a case where the outdoor temperature is low, frosting may occur on the outdoor heat exchanger 32.
  • the medium in the terminal heat exchange portion 17 may transfer heat to the third heat exchange portion 18, so as to increase the temperature of the first refrigerant and improve a defrosting speed of the outdoor heat exchanger 32, thereby improving the heating effect of the heat pump system.
  • the heat pump system may operate in the defrosting mode.
  • the heat pump system in a case where the temperature of the terminal heat exchange portion 17 is higher than the second preset temperature, the heat pump system may operate in the defrosting mode.
  • the heat pump system in a case where the temperature of the terminal heat exchange portion 17 is greater than or equal to 8 °C, the heat pump system operates in the defrosting mode.
  • the temperature of the terminal heat exchange portion 17 includes a temperature of water or other medium in the terminal heat exchange portion 17.
  • the heat pump system may operate periodically in the defrosting mode. For example, if the temperature of the terminal heat exchange portion 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 operating.
  • the first valve element 22 is configured to operate in the closed state, so as to close the passage between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13.
  • the third valve element 24 is configured to operate in the throttling state.
  • the four-way valve 31 in the low-temperature-stage circulation system changes a flow direction.
  • the first refrigerant in the third heat exchange portion 18 exchanges heat with water in the terminal heat exchange portion 17, and evaporates after absorbing heat.
  • the first valve element 22 closes the passage between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13
  • the first refrigerant after absorbing heat is unable to enter the low-temperature-stage circulation pipeline 13 through the cascade heat exchanger 11, but flows into the outdoor heat exchanger 32 after being compressed in the second compressor 30, and releases heat in the outdoor heat exchanger 32 to complete defrosting.
  • the first refrigerant passes through the third valve element 24 in the throttling state and returns to the terminal heat exchange portion 17.
  • a flow path of the first refrigerant is shown as F3 in FIG. 4 . It may be seen from FIGS.
  • the defrosting mode may also be referred to as a reverse cycle defrosting mode.
  • the first compressor 33 operates.
  • the first valve element 22 is configured to operate in the open state, so as to open the passage between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13.
  • the second valve element 23 is configured to operate in the throttling state, so as to open the passage between the second heat exchange portion 14 and the fourth heat exchange portion 19.
  • the third valve element 24 is configured to operate in the closed state, so as to close the passage between the third heat exchange portion 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 and evaporates, and then enters the second compressor 30 for compression.
  • the obtained high-temperature and high-pressure gaseous first refrigerant enters the first heat exchange portion 12 in the cascade heat exchanger 11.
  • the first heat exchange portion 12 operates in a condensation state
  • the second heat exchange portion 14 operates in an evaporation state.
  • the second refrigerant in the second heat exchange portion 14 absorbs the heat released by the first refrigerant in the first heat exchange portion 12, the second refrigerant evaporates and enters the first compressor 33 for compression.
  • the obtained high-temperature and high-pressure gaseous second refrigeration enters the fourth heat exchange portion 19, and exchanges heat with the water in the terminal heat exchange portion 17, so as to heat the water in the terminal heat exchange portion 17 to the set temperature, thereby achieving high-temperature heating of the heat pump system.
  • a flow path of the first refrigerant is shown as F1 in FIG. 5A
  • a flow path of the second refrigerant is shown as F2 in FIG. 5A .
  • the first valve element 22 is configured to operate in the open state, so as to open the passage between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13.
  • the second valve element 23 is configured to operate in the throttling state, so as to open the passage between the second heat exchange portion 14 and the fourth heat exchange portion 19.
  • the third valve element 24 is configured to operate in the open state, so as to open the passage between the third heat exchange portion 18 and the low-temperature-stage circulation pipeline 13.
  • the difference between the operation of the heat pump system in the rapid heating mode and the operation of the heat pump system in the high-temperature heating mode is that, the third valve element 24 is configured to operate in the open state in a case where the heat pump system operates in the rapid heating mode.
  • the high-temperature and high-pressure gaseous first refrigerant compressed by the second compressor 30 may enter the first heat exchange portion 12 of the cascade heat exchanger 11, and also enter the third heat exchange portion 18 for heat exchange with the terminal heat exchange portion 17.
  • the operating principle of the high-temperature and high-pressure gaseous first refrigerant entering the first heat exchange portion 12 of the cascade heat exchanger 11 for heat exchange is the same as that of the heat pump system operating in the high-temperature heating mode, and details will not be repeated herein.
  • the high-temperature-stage circulation system and the low-temperature-stage circulation system may be used to heat the water in the terminal heat exchange portion 17 simultaneously, so as to achieve the purpose of rapid heating.
  • a flow path of the first refrigerant is shown as F1 in FIG. 5B
  • a flow path of the second refrigerant is shown as F2 in FIG. 5B .
  • corresponding stop valves (27, 28) and valves (25, 26) may also be arranged at connecting pipelines between the heat pump indoor unit 10 and the heat pump outdoor unit 1.
  • the terminal heat exchange portion 17 may also be correspondingly provided with valves (20, 21) or valves (not shown in FIG. 2 ) for controlling connection of waterways.
  • the terminal heat exchange portion 17 may further include a first terminal heat exchange sub-portion 36 and a second terminal heat exchange sub-portion 37.
  • the first terminal heat exchange sub-portion 36 communicates with the second terminal heat exchange sub-portion 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, for example, a water fluorine heat exchanger.
  • the first terminal heat exchanger 34 includes the first terminal heat exchange sub-portion 36 and the third heat exchange portion 18, water in the first terminal heat exchange sub-portion 36 exchanges heat with the first refrigerant in the third heat exchange portion 18;
  • the second terminal heat exchanger 35 includes the second terminal heat exchange sub-portion 37 and the fourth heat exchange portion 19, water in the second terminal heat exchange sub-portion 37 exchanges heat with the second refrigeration in the fourth heat exchange portion 19.
  • the heat pump system may be used to produce high-temperature water, such as water higher than 60 °C.
  • the operating mode of the heat pump system is the high-temperature heating mode.
  • the first compressor 33 is operating.
  • the first valve element 22 is configured to operate in the open state, so as to open the passage between the first heat exchange portion 12 and the low-temperature-stage circulation pipeline 13.
  • the second valve element 23 is configured to operate in the throttling state, so as to open the passage between the second heat exchange portion 14 and the fourth heat exchange portion 19.
  • the third valve element 24 is configured to operate in the closed state, so as to close the passage between the third heat exchange portion 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 and evaporates, and then enters the second compressor 30 for compression, so as to form the high-temperature and high-pressure gaseous first refrigerant.
  • the high-temperature and high-pressure gaseous first refrigerant enters the first heat exchange portion 12.
  • the first heat exchange portion 12 operates in the condensation state
  • the second heat exchange portion 14 operates in the evaporation state.
  • the second refrigerant in the second heat exchange portion 14 exchanges heat with the first refrigerant in the first heat exchange portion 12, the second refrigerant absorbs heat and evaporates, and enters the first compressor 33 for compression after evaporating.
  • the formed high-temperature and high-pressure gaseous second refrigerant enters the fourth heat exchange portion 19 in the second terminal heat exchanger 36, and exchanges heat with the water in the second terminal heat exchange sub-portion 37, so as to heat the water to a temperature above 60 °C.
  • a flow path of the first refrigerant is shown as F4 in FIG. 6B
  • a flow path of the second refrigerant is shown as F5 in FIG. 6B .
  • the heat pump system shown in FIG. 6A may also operate in the low-temperature heating mode, the defrosting mode and the rapid heating mode.
  • the heat pump system may also operate in the low-temperature heating mode, the defrosting mode and the rapid heating mode.
  • the defrosting mode and the rapid heating mode For the operating principles of the heat pump system in a case where the heat pump system operates in the low-temperature heating mode, the defrosting mode and the rapid heating mode, reference may be made to the relevant descriptions in the FIGS. 3, 4 and 5B , and details will not be repeated herein.
  • the difference between the heat pump systems shown in FIGS. 6A and 6B is that there are other connection manners between the first terminal heat exchanger 34 and the second terminal heat exchanger 35.
  • the second valve element 23 may also be connected to a first port of the fourth heat exchange portion 19 and a first port of the second heat exchange portion 14.
  • An end of the first compressor 33 is connected to a second port of the fourth heat exchange portion 19, and another end of the first compressor 33 is connected to a second port of the second heat exchange portion 14.
  • the second valve element 23, the fourth heat exchange portion 19, the first compressor 33 and the second heat exchange portion 14 constitute the high-temperature-stage circulation system.
  • the heat pump outdoor unit 1 further includes a fourth valve element 104. As shown in FIGS. 7 and 9 , two ends of the fourth valve element 104 are connected to a first port of the third heat exchange portion 18 and a first port of the outdoor heat exchanger 32 respectively. A first end and a second end of the four-way valve 31 are connected to a second port of the first heat exchange portion 12 and a second port of the outdoor heat exchanger 32 respectively. A third end and a fourth end of the four-way valve 31 are connected to two ends of the second compressor 30 respectively. A second port of the third heat exchange portion 18 is connected to the second port of the first heat exchange portion 12.
  • the fourth valve element 104, the third heat exchange portion 18, the first heat exchange portion 12, the four-way valve 31, the second compressor 30 and the outdoor heat exchanger 32 constitute the low-temperature-stage circulation system.
  • the two ends of the fourth valve element 104 are connected to the second port of the first heat exchange portion 12 and the first port of the outdoor heat exchanger 32 respectively.
  • the first end and the second end of the four-way valve 31 are connected to the second port of the third heat exchange portion 18 and the second port of the outdoor heat exchanger 32 respectively.
  • the third end and the fourth end of the four-way valve 31 are connected to the two ends of the second compressor 30 respectively.
  • the first port of the third heat exchange portion 18 is connected to the first port of the first heat exchange portion 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.
  • an inlet of the water pump 402 is connected to the water inlet pipe, and an outlet of the water pump 402 is connected to an inlet of the first electric three-way valve 401.
  • a first outlet of the first electric three-way valve 401 is connected to a first port of the first terminal heat exchange sub-portion 36, and a second outlet of the first electric three-way valve 401 is connected to a first port of the second terminal heat exchange sub-portion 37.
  • a second port of the first terminal heat exchange sub-portion 36 and a second port of the second terminal heat exchange sub-portion 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 port of the first terminal heat exchange sub-portion 36.
  • the second port of the first terminal heat exchange sub-portion 36 is connected to the inlet of the first electric three-way valve 401, and the first outlet of the first electric three-way valve 401 is connected to the first port of the second terminal heat exchange sub-portion 37.
  • the second port of the second terminal heat exchange sub-portion 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 may also produce medium-temperature water and high-temperature water.
  • the temperature of the low-temperature water may be any value within a range of 40 °C to 60 °C
  • the temperature of the high-temperature water may be any value within a range of 60 °C to 80 °C.
  • the second compressor 30 operates, the first compressor 33 stops operating, 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 to say, the first electric three-way valve 401 is in a straight-through state.
  • the water in the water inlet pipe flows into the first terminal heat exchange sub-portion 36 through the water pump 402. In this case, the high-temperature and high-pressure gaseous first refrigerant compressed by the second compressor 30 passes through the first heat exchange portion 12.
  • the first refrigerant does not perform heat exchange in the cascade heat exchanger 11.
  • the first refrigerant in the first terminal heat exchanger 34 exchanges heat with the water in the first terminal heat exchange sub-portion 36, so as to produce hot water at a temperature of 40 °C to 60 °C.
  • Arrows in FIG. 10 may represent a direction of heat transfer during the production of medium-temperature water.
  • the first compressor 33 and the second compressor 30 operate, and the low-temperature-stage circulation system and the high-temperature-stage circulation system operate.
  • 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 to say, the first electric three-way valve 401 is in a bend-through state.
  • the water in the water inlet pipe flows into the second terminal heat exchange sub-portion 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 portion 12, and releases heat in the first heat exchange portion 12.
  • the second refrigerant in the second heat exchange portion 14 absorbs the heat released by the first heat exchange portion 12
  • the second refrigerant enters the fourth heat exchange portion 19.
  • the second refrigerant in the first terminal heat exchanger 35 exchanges heat with water in the second terminal heat exchange sub-portion 37, so as to produce hot water at a temperature of 60 °C to 80 °C.
  • the temperature of 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 high-temperature water may reach 80 °C.
  • Arrows in FIG. 11 may represent a direction of heat transfer during the production of high-temperature water.
  • FIG. 12 is a diagram showing an operating principle of the heat pump system shown in FIG. 7 in a case where the heat pump system operates in the defrosting mode. It may be seen from FIGS. 7 and 12 that, the operating principle of the heat pump system shown in FIG. 7 in a case where the heat pump system operates in the defrosting mode is similar to that in a case where the heat pump system operates in the low-temperature heating mode. The difference is that, the flow direction of the first refrigerant in a case where the heat pump system shown in FIG. 7 operates in the defrosting mode is opposite to that in a case where the heat pump system operates in the low-temperature heating mode. Arrows in FIG. 12 may represent a direction of heat transfer in the defrosting mode.
  • the heat pump system shown in FIGS. 8 and 9 may also operate in the low-temperature heating mode, the defrosting mode, the high-temperature heating mode, and the rapid heating mode.
  • the heat pump system shown in FIGS. 7 to 9 operating in different modes, reference may be made to the relevant descriptions in FIGS. 3 to 5B and FIGS. 10 to 12 , and details are not repeated herein.
  • the heat pump indoor unit may further include a temperature sensing assembly.
  • the temperature sensing assembly is configured to detect a temperature of the medium in the terminal heat exchange portion 17.
  • the heat pump system is configured to operate in the low-temperature heating mode, the defrosting mode, the high-temperature heating mode, or the rapid heating mode in response to the temperature of the medium in the terminal heat exchange portion 17 detected by the temperature sensing assembly.
  • 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 404.
  • the first temperature sensor 301 is disposed between the four-way valve 31 and the first heat exchange portion 12.
  • the second temperature sensor 302 is disposed between the first heat exchange portion 12 and the third heat exchange portion 18.
  • the third temperature sensor 303 is disposed between the third heat exchange portion 18 and the fourth valve element 104.
  • the fourth temperature sensor 304 is disposed at an outlet of the first compressor 33.
  • the fifth temperature sensor 305 is disposed between the fourth heat exchange portion 19 and the second valve element 23.
  • the sixth temperature sensor 403 is disposed between the water pump 402 and the first electric three-way valve 401.
  • the seventh temperature sensor 404 is disposed in the water outlet pipe.
  • 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 may be disposed in the heat pump outdoor unit 1.
  • the water pump 402, the first electric three-way valve 401, the cascade heat exchange portion 11, the terminal heat exchanger 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 a plurality of heat pump indoor units 10.
  • the heat pump indoor unit 10 and the heat pump outdoor unit 1 form a heat pump system with a one-to-one online mode.
  • 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 heat pump system with a one-to-multi online mode.
  • the heat pump indoor unit 10 may also be connected to a same heat pump outdoor unit 1 together with other indoor units (e.g., the indoor unit for ambient temperature adjustment), so as to form a multi-split heat pump system with a one-to-multi online mode.
  • other indoor units may be at least one air-cooling indoor unit 2, and the at least one air-cooling 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 end apparatuses 205, 206, 207.
  • the indoor end apparatuses 205, 206, 207 include a domestic hot water tank and at least one of space heating or cooling devices, and at least two of the indoor end apparatuses 205, 206, 207 switch with each other for operation.
  • the buffer water tank 202 includes a first water inlet A', a first water outlet B, a first return water inlet C and a second water outlet D.
  • the relay reversing device 201 has a second water inlet A' communicating with a water outlet of the terminal heat exchange portion 17, a third water outlet B' communicating with a return water inlet of the terminal heat exchange portion 17, and a second return water inlet C' and a fourth water outlet D' that communicate with main pipes of the indoor end apparatuses 205, 206, 207.
  • the relay reversing device 201 further includes a first straight-through path, a first bypass path, a second straight-through path and a second bypass path.
  • the first straight-through path directly communicates with the second water inlet A' and the fourth water outlet D'.
  • the first bypass path includes a first bypass sub-path and a second bypass sub-path.
  • the first bypass sub-path communicates with the second water inlet A' and the first water inlet A
  • the second bypass sub-path communicates with the first water outlet B and the fourth water outlet D'.
  • the first straight-through path communicates with the first bypass path in a switching manner, so as to achieve a communication pipeline from the terminal heat exchange portion 17 to the indoor end apparatuses 205, 206, 207.
  • the first bypass path is closed. In this case, the water flowing out from the water outlet of the terminal heat exchange portion 17 does not exchange heat through the buffer water tank 202.
  • the first straight-through path is closed. In this case, the water flowing out from the water outlet of the terminal heat exchange portion 17 exchanges heat through the buffer water tank 202.
  • the second straight-through path directly communicates with the second return water inlet C' and the third water outlet B'.
  • the second bypass path includes a third bypass sub-path and a fourth bypass sub-path.
  • the third bypass sub-path communicates with the second return water inlet C' and the first return water inlet C
  • the fourth bypass sub-path communicates with the second water outlet D and the third water outlet B'.
  • the second straight-through path communicates with the second bypass path in a switching manner, so as to achieve a communication pipeline from the indoor end apparatuses 205, 206, 207 to the terminal heat exchange portion 17.
  • the second bypass path is closed.
  • the water flowing from the indoor end apparatuses 205, 206, 207 back to the terminal heat exchange portion 17 does not exchange heat through the buffer water tank 202.
  • the second straight-through path is closed. In this case, the water flowing from the indoor end apparatuses 205, 206, 207 back to the terminal heat exchange portion 17 exchanges heat through the buffer water tank 202.
  • the relay reversing device 201 may switch between the straight-through path and the bypass path through the plurality of electric three-way valves or the plurality of check 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.
  • a first end of the second electric three-way valve 2011 communicates with the second water inlet A', a second end of the second electric three-way valve 2011 communicates with a first end of the third electric three-way valve 2012.
  • a second end of the third electric three-way valve 2012 communicates with the fourth water outlet D', a third end of the second electric three-way valve 2011 communicates with the first water inlet A, and a third end of the third electric three-way valve 2012 communicates with the first water outlet B.
  • the first straight-through path is formed.
  • the water flowing out from the water outlet of the terminal heat exchange portion 17 flows to sides of the indoor end apparatuses 205, 206, 207 through the first straight-through path.
  • the first bypass sub-path is formed in a case where the first end of the second electric three-way valve 2011 communicates with the third end of the second electric three-way valve 2011, the first bypass sub-path is formed.
  • the second bypass sub-path is formed in a case where the second end of the third electric three-way valve 2012 communicates with the third end of the third electric three-way valve 2012.
  • the water flowing out from the water outlet of the terminal heat exchange portion 17 flows to the indoor end apparatuses 205, 206, 207 through the first bypass sub-path, the buffer water tank 202 and the second bypass sub-path.
  • a first end of the fourth electric three-way valve 2013 communicates with the third water outlet B', and a second end of the fourth electric three-way valve 2013 communicates with a first end of the fifth electric three-way valve 2014.
  • a second end of the fifth electric three-way valve 2014 communicates with the second return water inlet C', a third end of the fourth electric three-way valve 2013 communicates with the second water outlet D, and a third end of the fifth electric three-way valve 2014 communicates with the first return water inlet C.
  • the second straight-through path is formed.
  • the return water on the sides of the indoor end apparatuses 205, 206, 207 flows back to the return water inlet of the terminal heat exchange portion 17 through the second straight-through path.
  • the third bypass sub-path is formed in a case where the first end of the fourth electric three-way valve 2013 communicates with the third end of the fourth electric three-way valve 2013, the third bypass sub-path is formed.
  • the fourth bypass sub-path is formed in a case where the second end of the fifth electric three-way valve 2014 communicates with the third end of the fifth electric three-way valve 2014.
  • the return water on the sides of the indoor end apparatuses 205, 206, 207 flows back to the return water inlet of the terminal heat exchange portion 17 through the fourth bypass sub-path, the buffer water tank 202 and the third bypass sub-path.
  • in a case of controlling the first straight-through path to open it is also necessary to control the second straight-through path to open; in a case of controlling the first bypass path to open, it is necessary to control the second bypass path to open correspondingly.
  • the relay reversing device 201 may also achieve the switching between the straight-through path and the bypass path through the plurality of check valves.
  • the relay reversing device 201 may include a first check valve, a second check valve, and a third check valve.
  • a first end of the first check valve is connected to the second water inlet A' and an end of the second check valve, and another end of the first check valve is connected to the fourth water outlet D' and an end of the third check valve.
  • Another end of the second check valve is connected to the first water inlet A, and another end of the third check valve is connected to the first water outlet B.
  • the first check valve In a case where the first check valve is closed, the first straight-through path is opened. In a case where the second check valve is closed, the first bypass sub-path is closed. In a case where the third check valve is closed, the second bypass sub-path is closed.
  • the plurality of check valves may also be used to form the second straight-through path, the third bypass sub-path and the fourth bypass sub-path, and the details will not be repeated herein.
  • the relay reversing device further includes a first force lift pump 2015 and a second force lift pump 2016.
  • the first force lift pump 2015 is disposed on the pipeline between the second water inlet A' and the second electric three-way valve 2011, so as to increase a pressure of the water in the pipeline.
  • the second force lift pump 2016 is disposed on the pipeline between the third electric three-way valve 2012 and the fourth water outlet D', so as to increase a pressure of the water in the pipeline.
  • the domestic hot water tank 206 and the space heating or cooling devices 205 and 207 may belong to the indoor end apparatuses with different types.
  • the domestic hot water tank 206 is in the heating mode when operating, but the space heating or cooling devices 205 and 207 may be in the heating mode or in the cooling mode when operating.
  • the electric three-way valve may be used to achieve the switching among the indoor end apparatuses 205, 206, 207.
  • an electric three-way valve 203 and an electric three-way valve 204 may be used to achieve the switching among the domestic hot water tank 206 and the space heating or cooling devices 205 and 207.
  • a first end of the electric three-way valve 203 communicates with the fourth water outlet D'
  • a second end of the electric three-way valve 203 communicates with a water inlet side of a fan coil 205
  • a third end of the electric three-way valve 203 communicates with a first end of the electric three-way valve 204.
  • a second end of electric three-way valve 204 communicates with a water inlet side of the domestic hot water tank 206, and a third end of the electric three-way valve 204 communicates with a water inlet side of a floor heating 207.
  • another electric three-way valve may be added correspondingly, and adjacent ports of the electric three-way valves are communicates with each other.
  • the plurality of check valves may also be used to form the switching operation among the indoor end apparatuses 205, 206, 207, and the details will not be repeated herein.
  • the operating principle of the relay reversing device 201 will be introduced below in a case where the domestic hot water tank 206 performs heating and the space heating or cooling devices 205, 207 perform cooling or heating switching, or the space heating or cooling devices 205, 207 switch between the cooling mode and the heating mode.
  • the buffer water tank 202 may be used as a heat storage device or a cold storage device.
  • the buffer water tank 202 is used as the heat storage device.
  • the relay reversing device 201 is controlled by collecting a water temperature and a target temperature of the indoor end apparatuses 205, 206, 207, so that the water flowing out from the water outlet of the terminal heat exchange portion 17 may exchange heat through or without the buffer water tank 202.
  • the relay reversing device 201 may be controlled by the heat pump indoor unit 10, or may be controlled by an independent controller.
  • the control of the independent controller may prevent the buffer water tank 202 from communicating with the auxiliary heat source in a case where the heat pump indoor unit 10 has malfunctioned, so as to provide heat source for the indoor end apparatuses 205, 206, 207.
  • the auxiliary heat source may be, for example, a gas wall mounted furnace, a solar water heater, or a gas water heater.
  • the relay reversing device 201 is controlled, so as to make the first bypass path communicate with the buffer water tank 202 (the first straight-through path is closed).
  • the heat of the water in the buffer water tank 202 is used to provide heat sources for the indoor end apparatuses 205, 206, 207.
  • the heat in the buffer water tank 202 is used to ensure the stable temperature during the space is heated, so as to improve user comfort.
  • the relay reversing device 201 is controlled, so as to make the first straight-through path open.
  • the water flowing out from the water outlet of the terminal heat exchange portion does not pass through the buffer water tank 202, so that the heating capacity of the heat pump system is used to provide the heat source for the indoor end apparatuses 205, 206, 207, and the pressure of the buffer water tank 202 is reduced.
  • the relay reversing device 201 is controlled, so as to make the first bypass path communicate with the buffer water tank 202.
  • the water flowing out from the water outlet of the terminal heat exchange portion passes through the buffer water tank 202, so as to make full use of the heat in the buffer water tank 202, so that the stable temperature during the space is heated may be ensured, and user comfort may be improved.
  • the heat pump system may further include an auxiliary heat source 102, and the auxiliary heat source 102 is used to provide 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 auxiliary heat source 102 operates, and the start and stop of the auxiliary heat source 102 may be controlled by the heat pump system.
  • the target temperature of the buffer water tank 202 for heating may be changed according to the different indoor end apparatuses 205, 206, 207.
  • the auxiliary heat source 102 and the heat pump indoor unit 10 may jointly provide heat for the water in the buffer water tank 202.
  • the relay reversing device 201 is controlled, so as to make the first straight-through path open.
  • the water flowing out from the water outlet of the terminal heat exchange portion 17 does not pass through the buffer water tank 202, so as to prevent the water for cooling from flowing into the buffer water tank 202.
  • the relay reversing device 201 is controlled, so as to make the first bypass path communicate with the buffer water tank 202.
  • the water flowing out from the water outlet of the terminal heat exchange portion 17 passes through the buffer water tank 202, so as to use the heat provided by the auxiliary heat source 102.
  • the auxiliary heat source 102 is the solar water heater
  • the water in the buffer water tank 202 may be heated in a case where a temperature condition that may be heated by solar energy is satisfied, so as to effectively use the energy.
  • the heat pump system may further include an alarm device.
  • the alarm device may give an alarm to remind the user in time.
  • the cooling mode may not be performed, but the heating mode may enter an emergency operation mode, so that the auxiliary heat source 102 may be used to heat the water in the buffer water tank 202, thereby meeting the heating demands of the indoor end apparatuses 205, 206, 207.
  • the buffer water tank 202 is used as the cold storage device.
  • the relay reversing device 201 is controlled, so as to make the first bypass path communicate with the buffer water tank 202.
  • the water flowing out from the water outlet of the terminal heat exchange portion 17 passes through the buffer water tank 202, so as to use the cold storage capacity of the buffer water tank 202, so that the water temperature may remain low for a long time and user comfort may be improved.
  • the relay reversing device 201 is controlled, so as to make the first straight-through path open.
  • the water flowing out from the water outlet of the terminal heat exchange portion 17 does not pass through the buffer water tank 202, so as to avoid changing the water in the buffer water tank 202 from cold water to hot water, thereby reducing the load of the buffer water tank 202 and avoiding energy waste.
  • the operating process of the switching among the domestic hot water tank 206 and three or more space heating or cooling devices is similar to the above.
  • the space heating or cooling devices switch with each other for operation.
  • the space heating or cooling device 205 e.g., the fan coil
  • the space heating or cooling device 207 e.g., the floor heating
  • the buffer water tank 202 is used as the heat storage device, for example, in winter, the heating switching process of the floor heating 207 and the fan coil 205 is as described in (1-1), and the details will not be repeated herein.
  • the buffer water tank is used as the cold storage device, for example, in summer or transition seasons, one of the fan coil 205 and the floor heating 207 is selected for cooling.
  • the relay reversing device 201 is controlled, so as to make the first bypass path communicate with the buffer water tank 202.
  • the water flowing out from the water outlet of the terminal heat exchange portion passes through the buffer water tank 202, so as to make full use of the cold storage capacity of the buffer water tank 202, so that the water temperature of the system may remain low for a long time and user comfort may be improved.
  • the plurality of space heating or cooling devices the operating process of the switching among the plurality of space heating or cooling devices is similar to the above, and the details will not be repeated herein.
  • the relay reversing device 201 by providing the relay reversing device 201 and the buffer water tank 202, it is possible to effectively reduce the pressure of the buffer water tank 202 while the different requirements of the indoor end apparatuses 205, 206, 207 are satisfied, thereby reducing energy loss and effectively improving user experience.
  • the heat pump indoor unit 10 may also include a pressure detecting device, a flow rate detecting device, a temperature detecting device, a water pump self-circulation pipeline, a water system full-circulation pipeline and a controller.
  • the pressure detecting device is used to detect an upstream pressure and a downstream pressure of the water pump 402.
  • the pressure detecting device includes a water pressure sensor 8-2 for detecting the upstream pressure of the water pump 402 and a water pressure sensor 8-1 for detecting the downstream pressure of the water pump 402.
  • the flow rate detecting device includes a water flow meter 9 for detecting a flow rate of the water pump 402.
  • the water pump self-circulation pipeline includes the water pump 402 and an electric regulating valve 5.
  • the water system full-circulation pipeline includes the water pump 402, a terminal heat exchanger 32 and the indoor end apparatus. That is to say, the water pump self-circulation pipeline and the water system full-circulation pipeline share a same water pump 402.
  • the water pump 402 may be a variable-speed pump.
  • the controller is coupled to the pressure detecting device and the flow rate detecting device, and is configured to perform a water pump characteristic test through the water pump self-circulation pipeline and a pipeline characteristic test through the water system full-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.
  • the switching between the water pump self-circulation pipeline and the water system full-circulation pipeline may be achieved through a 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 the temperature detecting device, and the temperature detecting device is used to detect an outlet water temperature and a return water temperature of the terminal heat exchange portion 17.
  • the temperature detecting 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 water system full-circulation pipeline, and an automatic exhaust valve 6-2 and a safety valve 7-2 located in the water pump self-circulation pipeline.
  • the water system full-circulation pipeline includes the water pump 402, the water pressure sensor 8-1, the electric three-way valve 3-1, the terminal heat exchanger 32, the automatic exhaust valve 6-1, the safety valve 7-1, the outlet water temperature sensor 501, the indoor end apparatus, the return water temperature sensor 502, the electric three-way valve 3-2, the water flow meter 9, and the water pressure sensor 8-2 that are connected in sequence by means of a pipeline.
  • the water pump self-circulation pipeline includes the water pump 402, the water pressure sensor 8-1, the electric three-way valve 3-1, the automatic exhaust valve 6-2, the safety valve 7-2, the electric regulating valve 5, the electric three-way valve 3-2, the water flow meter 9, and the water pressure sensor 8-2 that are connected in sequence by means of a pipeline.
  • the water pump 402 may achieve the automatic adjustment of different rotational speeds according to a control input parameter.
  • the electric three-way valve 3-1 and the electric three-way valve 3-2 may switch between different pipelines according to a control signal, so as to achieve the conversion of waterways.
  • the electric regulating valve 5 may have function of adjusting a plurality of opening degrees.
  • the automatic exhaust valve 6-1 and the automatic exhaust valve 6-2 may release excess air in the pipeline.
  • the safety valve 7-1 and the safety valve 7-2 release the pressure in a case where the pressure of the pipeline exceeds a limit value, so as to play a protective role.
  • the water pressure sensor 8-1 and the water pressure sensor 8-2 may collect the downstream water pressure and the upstream water pressure of the water pump 402 for resistance measurement, respectively.
  • the water flow meter 9 may detect a flow rate of the water flowing into and out from the water pump 402.
  • the outlet water temperature sensor 501 and the return water temperature sensor 502 are used to detect the outlet water temperature and the return water temperature of the terminal heat exchange portion 17 respectively, so as to participate in the adjustment of the rotational speed of the water pump during the constant temperature difference control.
  • the water pump self-circulation pipeline and the water system full-circulation pipeline include a first water supply port and a second water supply port, respectively.
  • the first water supply port includes a water supply port 1
  • the second water supply port includes a water supply 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 end apparatus 205 and the electric three-way valve 3-2.
  • the controller is configured to perform emptying control of the water pump before performing the water pump characteristic test and the pipeline characteristic test.
  • the heat pump indoor unit 10 may achieve automatic emptying of the water pump self-circulation pipeline and the automatic water pump characteristic test through the water pump self-circulation, and automatic emptying of the entire water system full-circulation pipeline and the automatic pipeline characteristic test through the water system full-circulation.
  • the heat pump outdoor unit 1 obtains heat from outdoor air or other media. After the refrigerant is compressed by the compressor, the refrigerant enters the terminal heat exchanger assembly 16 of the heat pump indoor unit 10, and exchanges heat with the terminal heat exchange portion 17, so as to heat the water in the terminal heat exchange portion 17.
  • An internal valve core of the electric three-way valve 3-1 is controlled to make a pipeline (6) communicate with a pipeline (7).
  • An internal valve core of the electric three-way valve 3-2 is controlled to make a pipeline (4) communicate with a pipeline (5).
  • the electric regulating valve 5 is fully closed, and the water pump 402 operates.
  • An electronic expansion valve 2 is controlled and adjusted according to a control rule of the heat pump system.
  • the refrigerant flows through a refrigerant gas pipe, a pipeline (1), a pipeline (2) and a pipeline (3) of the heat pump outdoor unit 1, and reaches a refrigerant liquid pipe of the heat pump outdoor unit 1, so that a refrigerant cycle loop is formed.
  • 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 of the liquid refrigerant is increased by the compressor, the liquid refrigerant releases the heat to the outdoor air.
  • the internal valve core of the electric three-way valve 3-1 is controlled to make the pipeline (6) communicate with the pipeline (7).
  • the internal valve core of the electric three-way valve 3-2 is controlled to make the pipeline (4) communicate with the pipeline (5).
  • the electric regulating valve 5 is fully closed, and the water pump 402 operates.
  • the electronic expansion valve 2 is controlled and adjusted according to a control rule of the heat pump system.
  • the refrigerant flows through the refrigerant liquid pipe, the pipeline (3), the pipeline (2), the pipeline (1), and the refrigerant air pipe of the heat pump outdoor unit 1, so that the refrigerant cycle loop is formed.
  • Such mode is suitable for the water resistance calibration during installation and debugging of a heat pump unit.
  • the heat pump system may start such mode only if the cooling mode or the heating mode is closed.
  • the internal valve core of the electric three-way valve 3-1 is controlled to make the pipeline (6) communicate with a pipeline (9).
  • the internal valve core of the electric three-way valve 3-2 is controlled to make a pipeline (10) communicate with the pipeline (5).
  • the electric regulating valve 5 is adjusted according to a set opening degree.
  • the water pump 402 operates.
  • the electronic expansion valve 2 is fully closed.
  • the refrigerant cycle loop is closed. Water in a portion of the system pipelines in the heat pump system flows through the pipeline (5), the pipeline (6), the pipeline (9), the pipeline (10), and the pipeline (5), so that the water system circulation flow path is formed.
  • the controller is used to replenish water through the water supply port 1 in a case where the downstream pressure P1 of the water pump is lower than a lower limit value M of a water system pressure after the water pump self-circulation mode starts; in a case where 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 operate intermittently until the downstream pressure P1 of the water pump 402 is between the lower limit value M and an upper limit value N of the water system pressure, and an absolute value of a difference between the downstream pressure of the water pump 402 at a first moment and the downstream pressure of the water pump 402 at a second moment is lower than a water pressure fluctuation limit value K within a third preset duration.
  • the first moment and the second moment may be any moment.
  • the second moment may be a moment before the first moment, such as the (n-1)-th moment.
  • the third preset duration may be any duration, for example, the third preset duration may be time t5.
  • the water supply port 1 may not be closed until the automatic emptying ends.
  • the controller controls the water pump 402 to operate intermittently, the rotational speeds of the water pump 402 at two adjacent times are different.
  • the water pump 402 may operate at a maximum rotational speed, or at any rotational speed lower than the maximum rotational speed.
  • the water pump 402 may operate at A of the maximum rotational speed, where A is a value greater than 0 and less than 1.
  • a water pump emptying control method of the heat pump unit before the water pump characteristic test includes step 1 to step 11.
  • step 1 the water pump self-circulation starts.
  • step 2 it is determined whether P1 is greater than M (P1 > M); if so, step 4 is performed; if not, step 3 is performed.
  • step 3 water is replenished through the water supply port 1, and step 2 is performed.
  • step 4 the water pump 402 operates at the maximum rotational speed. Time t1 elapses.
  • step 5 the water pump 402 stops operating. Time t2 elapses.
  • step 6 the water pump 402 operates at A of the maximum rotational speed. Time t3 elapses.
  • step 7 the water pump 402 stops operating. Time t4 elapses.
  • step 8 the water pump 402 operates at the maximum rotational speed.
  • step 9 it is determined whether P1 is greater than M and less than N (M ⁇ P1 ⁇ N); if so, step 10 is performed; if not, step 4 is performed.
  • step 10 it is determined whether an absolute value of a difference between P1(n) and P1(n-1) is less than K (
  • step 11 the emptying control is completed.
  • the water pump characteristic test may be performed.
  • the controller performs the water pump characteristic test through the water pump self-circulation pipeline, and the method includes: first, controlling the water pump self-circulation pipeline to open, controlling the water pump to operate at a first rotational speed, and controlling the electric regulating valve 5 at a first opening degree corresponding to the first rotational speed within a first preset duration; then, calculating an average of differences between the downstream pressures and the upstream pressures detected by the pressure detecting device within the first preset duration, so as to obtain first operating parameters, the first operating parameters corresponding to a lift of the water pump, and the first operating parameters including the first rotational speed and the first opening degree; next, calculating an average of the flow rates detected by the flow rate detecting device within the first preset duration, so as to obtain an average of the flow rates of the water pump corresponding to the first operating parameters; finally, obtaining a test result of the water pump characteristic test according to the lifts of the water pump corresponding to the plurality of operating parameters and the averages of the flow rates of the water pump corresponding to the plurality of operating
  • the water pump 402 may include a plurality of first rotational speeds. Each rotational speed may correspond to a plurality of opening degrees of the electric regulating valve 5, and it is required that the water pump 402 operates for a set duration at the opening degrees corresponding to each rotational speed.
  • the average ⁇ P of differences between the downstream pressures and upstream pressures detected by the pressure detecting device within the set duration is calculated, and ⁇ P is the lift of the water pump; meanwhile, the average Q of the flow rates detected by the flow rate detecting device in each rotational speed within the set duration is calculated.
  • the first preset duration may be any duration.
  • the first preset duration may be time t11.
  • step 1 the emptying control is completed.
  • step 2 the water pump 402 operates at the maximum rotational speed.
  • step 3 a program 1 that the electric regulating valve 5 is fully closed and then is opened (at 20% opening degree) is performed. After time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to a coordinate point of the electric regulating valve 5 at the 20% opening degree shown in FIG. 24 .
  • step 4 a program 2 that the electric regulating valve 5 is opened (at 50% opening degree) is performed. After time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to a coordinate point of the electric regulating valve 5 at the 50% opening degree shown in FIG. 24 .
  • step 5 a program 3 that the electric regulating valve 5 is opened (at 70% opening degree) is performed. After time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to a coordinate point of the electric regulating valve 5 at the 70% opening degree shown in FIG. 24 .
  • step 6 a program 4 that the electric regulating valve 5 is opened (at 100% opening degree) is performed. After time t11 elapses, ⁇ P and Q are calculated, and the ⁇ P and Q correspond to a coordinate point of the electric regulating valve 5 at the 100% opening degree shown in FIG. 24 .
  • the water pump characteristic curve corresponding to the maximum rotational speed of the water pump 402 may be obtained according to the coordinate point of the electric regulating valve 5 at the 20% opening degree shown in FIG. 24 , the coordinate point of the electric regulating valve 5 at the 50% opening degree shown in FIG. 24 , the coordinate point of the electric regulating valve 5 at the 70% opening degree shown in FIG. 24 , and the coordinate point of the electric regulating valve 5 at the 100% opening degree shown in FIG. 24 in a case where the water pump 402 operates at the maximum rotational speed.
  • step 7 the water pump 402 operates at 75% of the maximum rotational speed.
  • step 8 step 3 to step 7 are repeated.
  • step 3 to step 7 are repeated, so as to obtain a water pump characteristic curve corresponding to 75% of the maximum rotational speed of the water pump 402.
  • step 9 the water pump 402 operates at 50% of the maximum rotational speed. If the rotational speed of the water pump reaches a set lower limit rotational speed of the water pump, the test ends after the operation is completed.
  • step 10 step 3 to step 7 are repeated.
  • step 3 to step 7 are repeated, so as to obtain a water pump characteristic curve corresponding to 50% of the maximum rotational speed of the water pump 402.
  • step 11 the water pump 402 operates at 25% of the maximum rotational speed, the curve corresponding to 25% of the maximum rotational speed of the water pump 402 is as shown in FIG. 24 . If the rotational speed of the water pump reaches the set lower limit rotational speed of the water pump, the test ends after the operation is completed.
  • step 12 step 3 to step 7 are repeated.
  • step 3 to step 7 are repeated, so as to obtain a water pump characteristic curve corresponding to 25% of the maximum rotational speed of the water pump 402.
  • step 13 the water pump 402 operates at the lower limit rotational speed, the curve corresponding to the lower limit rotational speed of the water pump 402 is as shown in FIG. 24 .
  • step 14 step 3 to step 7 are repeated.
  • step 3 to step 7 are repeated, so as to obtain a water pump characteristic curve corresponding to the lower limit rotational speed of the water pump 402.
  • step 15 the automatic water pump characteristic test ends.
  • the heat pump system automatically draws the water pump characteristic curves according to the data of the automatic water pump characteristic test.
  • the curves are embedded in an internal program of the heat pump system, or may also be displayed on an interface of a user-side controller, which is convenient for installation and maintenance people to check the waterway.
  • Such mode is suitable for the water resistance calibration during installation and debugging of the heat pump unit.
  • the heat pump system may perform such mode only in a case where the cooling mode or the heating mode is closed.
  • the internal valve core of the electric three-way valve 3-1 is controlled to make the pipeline (6) communicate with the pipeline (7).
  • the internal valve core of the electric three-way valve 3-2 is controlled to make the pipeline (4) communicate with the pipeline (5).
  • the electric regulating valve 5 is fully closed.
  • the water pump 402 operates.
  • the electronic expansion valve 2 is fully closed.
  • the refrigerant cycle loop is closed. Water in a portion of the system pipelines in the heat pump system flows through the pipeline (5), the pipeline (6), the pipeline (7), the pipeline (8), the pipeline (4), and the pipeline (5), so that the water system circulation flow path is formed.
  • the controller is used to replenish water through the water supply port 2 in a case where the downstream pressure P1 of the water pump is lower than the lower limit value M of the water system pressure after the water system full-circulation mode starts; in a case where 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 operate intermittently until the downstream pressure P1 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 absolute value of the differences between the downstream pressures of the water pump 402 at the first moment and the downstream pressures of the water pump 402 at the second moment is lower than the water pressure fluctuation limit value K within the third preset duration.
  • the first moment and the second moment may be any moment.
  • the second moment may be a moment before the first moment, such as the (n-1)-th moment.
  • the third preset duration may be any duration, for example, the third preset duration may be the time t5.
  • the water supply port 2 may not be closed until the automatic emptying ends.
  • the controller controls the water pump 402 to operate intermittently, the rotational speeds of the water pump 402 at two adjacent times are different.
  • the water pump 402 may operate at the maximum rotational speed, or at any rotational speed lower than the maximum rotational speed.
  • the water pump 402 may operate at A of the maximum rotational speed, 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 as following.
  • step 1 the water system full-circulation starts.
  • step 2 it is determined whether P1 is greater than M (P1 > M); if so, step 4 is performed; if not, step 3 is performed.
  • step 3 water is replenished through the water supply port 2, and step 2 is performed.
  • step 4 the water pump 402 operates at the maximum rotational speed. Time t6 elapses.
  • step 5 the water pump 402 stops operating. Time t7 elapses.
  • step 6 the water pump 402 operates at A of the maximum rotational speed. Time t8 elapses.
  • step 7 the water pump 402 stops operating. Time t9 elapses.
  • step 8 the water pump 402 operates at the maximum rotational speed.
  • step 9 it is determined whether P1 is greater than M and less than N (M ⁇ P1 ⁇ N); if so, step 10 is performed; if not, step 4 is performed.
  • step 10 it is determined whether an absolute value of a difference between P1(n) and P1(n-1) is less than K (
  • step 11 the emptying control is completed.
  • the pipeline characteristic test may be performed.
  • the controller performs the pipeline characteristic test through the water system full-circulation pipeline, and the method includes: first, controlling the water system full-circulation pipeline to open, controlling the water pump to operate at a second rotational speed for a second preset duration; then, calculating an average of differences between the downstream pressures and the upstream pressures detected by the pressure detecting device within the second preset duration, so as to obtain a pipeline resistance corresponding to the second rotational speed; next, calculating an average of the flow rates detected by the flow rate detecting device within the second preset duration, so as to obtain an average of the flow rates corresponding to the second rotational speed; finally, obtaining a test result of the pipeline characteristic test according to the pipeline resistances corresponding to the plurality of rotational speeds and the averages of the flow rates corresponding to the plurality of rotational speeds, and the test result of the pipeline characteristic test including a pipeline characteristic curve.
  • the water pump 402 may include a plurality of second rotational speeds, and it is required that the water pump 402 operates for a set duration at each rotational speed.
  • the average ⁇ P' of differences between the downstream pressures and the upstream pressures detected by the pressure detecting device within the set duration is calculated, and ⁇ P' is the pipeline resistance; meanwhile, the average Q' of the flow rates detected by the flow rate detecting device within the set duration is calculated.
  • the second preset duration may be any duration.
  • the second preset duration may be time t12. The method for the pipeline characteristic test is described below with reference to FIG. 26 .
  • step 1 the emptying control is completed.
  • step 2 the water pump 402 operates at the maximum rotational speed.
  • time t12 elapses, ⁇ P' and Q' are calculated, and the ⁇ P' and Q' correspond to a coordinate point of the maximum rotational speed of the water pump 402 shown in FIG. 27 .
  • step 3 the water pump 402 operates at 75% of the maximum rotational speed.
  • time t12 elapses, ⁇ P' and Q' are calculated, and the ⁇ P' and Q' correspond to a coordinate point of 75% of the maximum rotational speed of the water pump 402 shown in FIG. 27 .
  • step 4 the water pump 402 operates at 50% of the maximum rotational speed.
  • time t12 elapses, ⁇ P' and Q' are calculated, and the ⁇ P' and Q' correspond to a coordinate point of 50% of the maximum rotational speed of the water pump 402 shown in FIG. 27 .
  • step 5 the water pump 402 operates at 25% of the maximum rotational speed.
  • time t12 elapses, ⁇ P' and Q' are calculated, and the ⁇ P' and Q' correspond to a coordinate point of 25% of the maximum rotational speed of the water pump 402 shown in FIG. 27 .
  • the pipeline characteristic curve may be obtained according to the coordinate point of the maximum rotational speed of the water pump 402 shown in FIG. 24 , the coordinate point of 75% of the maximum rotational speed of the water pump 402, the coordinate point of 50% of the maximum rotational speed of the water pump 402, and the coordinate point of 50% of the maximum rotational speed of the water pump 402.
  • step 6 the automatic water pump characteristic test ends.
  • the heat pump system automatically draws the pipeline characteristic curve according to the data of the automatic pipeline characteristic test.
  • the curves are embedded in the internal program of the heat pump system, or may also be displayed on the interface of the user-side controller, which is convenient for installation and maintenance people to check the waterway.
  • the heat pump system may define three different water pump control functions such as constant rotational speed, constant water volume and constant water temperature difference in the heating mode and the cooling mode.
  • the water pump 402 operates according to a set rotational speed.
  • the rotational speed of water pump 402 is adjusted through frequency conversion, so as to keep the water flow rate in the circulation of the heat pump system at a set value.
  • the rotational speed of water pump 402 is adjusted through frequency conversion, so as to keep the water temperature difference (in the cooling mode, the water temperature difference is equal to a difference between a return water temperature and an outlet water temperature; in the heating mode, the water temperature difference is equal to a difference between the outlet water temperature and the return water temperature) of the heat pump system at a set value.
  • the user may set different maximum rotational speed and lower limit rotational speed of the water pump according to requirements.
  • Such function is suitable for a case where the heat pump system normally operates in the cooling mode or the heating mode.
  • the heat pump system may perform such function only in a case where the cooling mode or the heating mode starts.
  • the water pump 402 operates at a set rotational speed.
  • the internal valve core of the electric three-way valve 3-1 is controlled, so as to make the pipeline (6) communicate with the pipeline (7).
  • the internal valve core of the electric three-way valve 3-2 is controlled, so as to make the pipeline (4) communicate with the pipeline (5).
  • the electric regulating valve 5 is fully closed.
  • the water pump 402 operates at the set rotational speed.
  • the electronic expansion valve 2 is controlled and adjusted according to a control rule of the heat pump system.
  • the constant rotational speed control method is as following.
  • step 1 a user sets a rotational speed on an operating interface.
  • the operating rotational speed of the water pump 402 defaults to the maximum rotational speed. If the user does not actively set a rotational speed, the water pump 402 operates at the maximum rotational speed.
  • step 2 the cooling mode or the heating mode starts.
  • step 3 the water pump 402 operates at the set rotational speed.
  • step 4 the cooling mode or the heating mode is closed.
  • Time t13 elapses, and time t13 is a duration when the water pump delays in stopping, the unit is second.
  • step 5 the water pump 402 stops operating.
  • Such function is suitable for a case where the heat pump system normally operates in the cooling mode or the heating mode. Such function is performed only in a case where the cooling mode or the heating mode starts.
  • the internal valve core of the electric three-way valve 3-1 is controlled, so as to make the pipeline (6) communicate with the pipeline (7).
  • the internal valve core of the electric three-way valve 3-2 is controlled, so as to make the pipeline (4) communicate with the pipeline (5).
  • the electric regulating valve 5 is fully closed.
  • the water pump 402 operates.
  • An electronic expansion valve 2 is controlled and adjusted according to a control rule of the heat pump system.
  • the unit installation or maintenance people may set the water flow rate required for the operation of the heat pump system according to requirements.
  • the heat pump system draws a water pump and pipeline characteristic curve according to the water pump characteristic curve measured in the water pump self-circulation mode ( FIG. 24 ) and the pipeline characteristic curve measured in the water system full-circulation mode ( FIG. 27 ), and the water pump and pipeline characteristic curve is as shown in FIG. 29 .
  • the controller is further configured to: firstly, obtain a target water flow rate; then obtain a rotational speed corresponding to the target water flow rate according to the target water flow rate and the pipeline characteristic curve; finally, control the water pump to operate at the rotational speed corresponding to the target water flow rate.
  • the target water flow rate is the required water flow rate.
  • the target water flow rate is the required water flow rate set by the user.
  • a corresponding operating point on the pipeline characteristic curve is obtained according to the required water flow rate, and a rotational speed of the water pump corresponding to the water pump characteristic curve passing through the operating point is selected as a target rotational speed of the water pump, which is used to control the operation of the water pump.
  • the heat pump system first obtains a corresponding operating point (e.g., the operating point 1) on the pipeline characteristic curve through the water flow rate, and selects the water pump characteristic curve (25% of the maximum rotational speed of water pump 4) passing through the operating point, and the rotational speed of the water pump corresponding to the curve (25% of the maximum rotational speed of water pump 4) may be used as the determined rotational speed of the water pump.
  • a corresponding operating point e.g., the operating point 1
  • the water pump characteristic curve 25% of the maximum rotational speed of water pump 4
  • the controller may also perform linear interpolation on adjacent water pump characteristic curves, so as to obtain the target rotational speed of the water pump.
  • the heat pump system first obtains a corresponding operating point (e.g., the operating point 2) on the pipeline characteristic curve through the water flow rate. If the operating point is not on the measured water pump characteristic curves, the heat pump system performs linear interpolation on adjacent water pump characteristic curves (the curve of 25% of the maximum rotational speed of the water pump 4 and the curve of lower limit rotational speed of the water pump 4), so as to finally obtain the appropriate rotational speed of the water pump.
  • a corresponding operating point e.g., the operating point 2
  • adjacent water pump characteristic curves the curve of 25% of the maximum rotational speed of the water pump 4 and the curve of lower limit rotational speed of the water pump 4
  • the rotational speed of the water pump is dynamically adjusted according to the real-time data detected by the water flow meter 9, and the process is as shown in FIG. 30 .
  • step 1 the water pump 402 operates at a rotational speed corresponding to a constant water flow rate. Time t14 elapses.
  • Such function is suitable for a case where the heat pump system normally operates in the cooling mode or the heating mode.
  • the heat pump system may perform such mode only in a case where the cooling mode or the heating mode starts.
  • the internal valve core of the electric three-way valve 3-1 is controlled, so as to make the pipeline (6) communicate with the pipeline (7).
  • the internal valve core of the electric three-way valve 3-2 is controlled, so as to make the pipeline (4) communicate with the pipeline (5).
  • the electric regulating valve 5 is fully closed.
  • the water pump 402 operates.
  • the electronic expansion valve 2 is controlled and adjusted according to a control rule of the air source heat pump.
  • the controller is further configured to: firstly, obtain a water temperature difference required by the user; then, obtain a current water temperature difference according to a current outlet water temperature and a current return water temperature of the terminal heat exchange portion; next, calculate a target water flow rate according to the current water temperature difference, a current water flow rate detected by the flow rate detecting device, and the water temperature difference required by the user; finally, control the water pump to operate at a preset maximum rotational speed, and after the water pump operates stably, control the water pump to operate at a target rotational speed corresponding to the target water flow rate.
  • the target water flow includes a required water flow rate, which is determined by the current water temperature difference and the current water flow rate.
  • the operation of the water pump 402 is controlled by obtaining the target rotational speed of the water pump according to the required water flow rate.
  • the unit installation or maintenance people may set the water temperature difference required for the operation of the heat pump system (in the cooling mode, the water temperature difference is equal to the difference between the return water temperature and the outlet water temperature; in the heating mode, the water temperature difference is equal to the difference between the outlet water temperature and the return water temperature) according to requirements.
  • the water pump 402 operates at a set maximum rotational speed.
  • a rotational speed of the water pump corresponding to initial constant temperature difference is obtained through the same control method as the constant water flow rate function.
  • the rotational speed of the water pump is dynamically adjusted according to the temperature values detected by the outlet water temperature sensor 501 and the return water temperature sensor 502, and the process is as shown in FIG. 31 .
  • step 1 the water pump 402 operates at a rotational speed corresponding to a constant water temperature difference. Time t15 elapses.
  • ⁇ R'(n) ⁇ R3(n) + ⁇ R4(n).
  • the present disclosure may achieve the water pump characteristic test and the pipeline characteristic test through the heat pump system as shown in FIG. 21 , and achieve the automatic adjustment of the rotational speed of the water pump according to the test results without repeated debugging. Moreover, constant rotational speed control, constant water flow rate control, and constant water temperature difference control of the heat pump system may also be achieved according to requirements of the user.
  • Some embodiments of the present disclosure provide a control method of a heat pump system, and the heat pump system may be the heat pump system described in any of the above embodiments. As shown in FIG. 32 , the control method of the heat pump system includes step 321 to step 324.
  • step 321 it is determined whether the heat pump system satisfies a preset condition; the preset condition includes a low-temperature heating condition, a defrosting condition, a high-temperature heating condition or a rapid heating condition.
  • step 322 the terminal heat exchange portion is controlled to exchange heat with the third heat exchange portion if the heat pump system satisfies the low-temperature heating condition or the defrosting condition.
  • the low-temperature heating condition includes but is not limited to a set temperature being lower than a first preset temperature; the defrosting condition includes but is not limited to a temperature of the terminal heat exchange portion 17 being higher than a second preset temperature, and the second preset temperature may be, for example, 8 °C.
  • the first compressor 33 in a case where the heat pump system satisfies 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 while the first valve element 22 and the second valve element 23 are controlled to be closed, and the third valve element 24 is controlled to open.
  • step 323 the terminal heat exchange portion is controlled to exchange heat with the fourth heat exchange portion if the heat pump system satisfies the high-temperature heating condition.
  • the high-temperature heating condition includes that the set temperature is higher than a third preset temperature.
  • the first compressor 33 is controlled to operate; or the first compressor 33 is controlled to operate while the first valve element 22 and the second valve element 23 are controlled to communicate with each other and the third valve element 24 is controlled to be closed.
  • step 324 the terminal heat exchange portion is controlled to exchange heat with the third heat exchange portion and the fourth heat exchange portion if the heat pump system satisfies the rapid heating condition.
  • the rapid heating condition includes that the heat pump system is required to be heated to a fourth preset temperature within a short time. For example, in a case where the water heater is turned on and the set temperature is 40 °C, the heat pump system is required to be heated to 40 °C within a short time.
  • the first compressor 33 is controlled to operate; or, the first compressor 33 is controlled to operate while the first valve element 22, the second valve element 23 and the third valve element 24 are controlled to communicate with each other.
  • the terminal heat exchange portion is controlled to perform heat exchange with the third heat exchange portion.
  • the low-temperature-stage circulation system operates and the high-temperature-stage circulation system stops.
  • the control method of the heat pump system provided by the embodiments of the present disclosure may avoid a problem of low reliability of system operation caused by insufficient pressure difference in the high-temperature-stage circulation system by controlling the high-temperature-stage circulation system to stop operating, so as to ensure the reliable operation of the heat pump system. That is to say, the control method of the heat pump system provided by the embodiments of the present disclosure may independently control whether the low-temperature-stage circulation system and the high-temperature-stage circulation system operate, so as to achieve high flexibility and low energy consumption.

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
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EP22819590.5A 2021-06-08 2022-06-08 Système de pompe à chaleur et procédé de commande associé Pending EP4354048A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
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.XA CN113432172A (zh) 2021-06-25 2021-06-25 热泵机组室内单元和热泵机组
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
PCT/CN2022/097721 WO2022257993A1 (fr) 2021-06-08 2022-06-08 Système de pompe à chaleur et procédé de commande associé

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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
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

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KR20110056061A (ko) * 2009-11-20 2011-05-26 엘지전자 주식회사 히트 펌프식 급탕장치
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
CN103076080B (zh) * 2013-01-06 2014-12-24 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
CN108072173B (zh) * 2018-01-23 2024-01-30 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

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