EP1777471A1 - Dispositif d'alimentation en eau chaude de type pompe à chaleur - Google Patents

Dispositif d'alimentation en eau chaude de type pompe à chaleur Download PDF

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Publication number
EP1777471A1
EP1777471A1 EP05765649A EP05765649A EP1777471A1 EP 1777471 A1 EP1777471 A1 EP 1777471A1 EP 05765649 A EP05765649 A EP 05765649A EP 05765649 A EP05765649 A EP 05765649A EP 1777471 A1 EP1777471 A1 EP 1777471A1
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EP
European Patent Office
Prior art keywords
pressure
refrigerant
temperature
target
temperature difference
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.)
Withdrawn
Application number
EP05765649A
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German (de)
English (en)
Inventor
Jouji Kuroki
Hisayoshi Sakakibara
Teruhiko Taira
Susumu Kawamura
Masato Murayama
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.)
Denso Corp
Original Assignee
Denso Corp
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Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Publication of EP1777471A1 publication Critical patent/EP1777471A1/fr
Withdrawn legal-status Critical Current

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    • 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
    • F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
    • F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
    • 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
    • F24H15/215—Temperature of the water before heating
    • 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
    • F24H15/219—Temperature of the water after heating
    • 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
    • F24H15/227—Temperature of the refrigerant in heat pump cycles
    • 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
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/258—Outdoor temperature
    • 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
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat 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
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/38—Control of compressors of heat 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
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/385—Control of expansion valves of heat pumps
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2600/17—Control issues by controlling the pressure 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
    • F25B2700/19—Pressures
    • 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
    • F25B2700/2102—Temperatures at the outlet of the gas cooler
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present invention relates to a heat pump type water heater using a heat pump cycle as a heating means for heating water for hot-water supply, and more particular, relative to a method of controlling a pressure reducing means at the time of a boiling-up operation.
  • a pressure reducing means controls pressure of a refrigerant on a high-pressure side so that a temperature difference ⁇ T between temperature of a refrigerant flowing from a gas cooler (radiator), which heats water for hot-water supply, and temperature of water for hot-water supply, flowing into the gas cooler becomes a predetermined temperature difference ⁇ To.
  • a gas cooler radiator
  • the invention has been thought of in view of the problem and has an object to provide a heat pump type water heater, in which stability of a cycle relative to external factors is high.
  • a heat pump type water heater is for heating water for hot-water supply in a vapor-compression type heat pump cycle in which heat on a low-temperature side is transferred to a high-temperature side.
  • the heat pump type water heater includes a compressor (1) that sucks and compresses refrigerant; a radiator (2) constructed such that heat exchange is performed between refrigerant discharged from the compressor (1) and water for hot-water supply and a flow of refrigerant and a flow of water for hot-water supply are opposed to each other; pressure reducing means (3, 30) that reduces pressure of refrigerant flowing from the radiator (2); and an evaporator (4), in which refrigerant flowing from the pressure reducing means (3, 30) is evaporated by absorbing heat and refrigerant is discharged to flow to a suction side of the compressor (1).
  • a refrigerant pressure on a high-pressure side is controlled such that when refrigerant pressure on the high-pressure side is less than a predetermined pressure, an actual temperature difference ( ⁇ T) between a refrigerant temperature flowing from the radiator (2) and a water temperature flowing into the radiator (2) becomes a predetermined target temperature difference ( ⁇ Tt).
  • ⁇ T actual temperature difference
  • ⁇ Tt target temperature difference
  • stability of the cycle relative to a variation in the heat pump cycle, which is caused by external factors, can be improved by directly controlling the pressure reducing means (3, 30) based on a high pressure value detected by a pressure sensor having a good response or the like.
  • the pressure sensor since the pressure sensor involves a large dispersion in detection values, it is difficult to obtain a target COP.
  • the target COP can be obtained by correcting the target pressure (Pt) on the basis of an actual temperature difference ( ⁇ T) detected by the temperature sensor, which is small in dispersion. Since a control of the pressure reducing valve is made possible even when either of the pressure sensor and the temperature sensor is abnormal, reliability of a system can be improved on a user's side.
  • a heat pump type water heater is for heating water for hot-water supply in a vapor-compression type heat pump cycle in which heat on a low-temperature side is transferred to a high-temperature side.
  • the heat pump type water heater includes: a compressor (1) that sucks and compresses refrigerant; a radiator (2) constructed such that heat exchange is performed between refrigerant discharged from the compressor (1) and water for hot-water supply and a flow of refrigerant and a flow of water for hot-water supply are opposed to each other; pressure reducing means (3, 30) that reduces pressure of refrigerant flowing from the radiator (2); and an evaporator (4), in which refrigerant flowing from the pressure reducing means (3, 30) is evaporated by absorbing heat and refrigerant is discharged to flow to a suction side of the compressor (1) .
  • a refrigerant pressure on a high-pressure side is controlled such that when the refrigerant pressure on the high-pressure side is less than a predetermined pressure, an actual temperature difference ( ⁇ T) between a refrigerant temperature flowing from the radiator (2) and a water temperature flowing into the radiator (2) becomes a predetermined target temperature difference ( ⁇ Tt).
  • ⁇ T actual temperature difference
  • ⁇ Tt target temperature difference
  • stability of the cycle relative to a variation in the heat pump cycle, which is caused by external factors, can be improved by directly controlling pressure reducing means (3, 30) based on a high pressure value detected by a pressure sensor having a good response or the like.
  • the pressure sensor involves a large dispersion in detection values and is difficult to obtain a target COP.
  • the target COP can be obtained by correcting a target pressure (Pt) on the basis of an actual discharge temperature (T) detected by the temperature sensor, which is small in dispersion. Since a control of the pressure reducing valve is made possible even when either of the pressure sensor and the temperature sensor is abnormal, reliability of a system can be improved on a user's side.
  • a control of setting the target pressure (Pt), controlling the refrigerant pressure on the high-pressure side to approach the target pressure (Pt), calculating the temperature difference ( ⁇ T1) between the target temperature difference ( ⁇ Tt) and the actual temperature difference ( ⁇ T), and correcting the target pressure (Pt) to make the temperature difference ( ⁇ T1) equal to or less than a predetermined value is performed when at least one of an outside air temperature, an inlet refrigerant temperature of the evaporator (4), and an outlet refrigerant temperature of the evaporator (4) is less than a predetermined value.
  • stability of the cycle can be improved by performing the high-pressure F/B pressure reducing valve control with the use of the pressure sensor at the time of low temperature when at least one of the outside air temperature, the inlet refrigerant temperature of the evaporator (4), and the outlet refrigerant temperature of the evaporator (4) is lower than a predetermined value (for example, 0°C or lower).
  • the boiling-up operation is performed by the high-pressure F/B pressure reducing valve control corresponding to a target COP at the time of high temperature when at least one of the outside air temperature, the inlet refrigerant temperature of the evaporator (4), and the outlet refrigerant temperature of the evaporator (4) is higher than the predetermined value (for example, over 0°C).
  • the target COP can be obtained by the high-pressure F/B pressure reducing valve control that uses a value of the temperature sensor.
  • a control of setting the target pressure (Pt), controlling the refrigerant pressure on the high-pressure side to approach the target pressure (Pt), setting the target discharge temperature (Tt) of refrigerant discharged from the compressor (1), calculating a temperature difference ( ⁇ T2) between the target discharge temperature (Tt) and the actual discharge temperature (T), and correcting the target pressure (Pt) to make the temperature difference ( ⁇ T2) equal to or less than a predetermined value is performed when at least one of an outside air temperature, an inlet refrigerant temperature of the evaporator (4), and an outlet refrigerant temperature of the evaporator (4) is less than a predetermined value.
  • stability of the cycle can be improved by performing the high-pressure F/B pressure reducing valve control with the use of the pressure sensor at the time of low temperature (for example, 0°C or lower) when at least one of the outside air temperature, the inlet refrigerant temperature of the evaporator (4), and the outlet refrigerant temperature of the evaporator (4) is lower than a predetermined value.
  • low temperature for example, 0°C or lower
  • the boiling-up operation is performed by the high-pressure F/B pressure reducing valve control corresponding to the target COP at the time of high temperature when at least one of the outside air temperature, the inlet refrigerant temperature of the evaporator (4), and the outlet refrigerant temperature of the evaporator (4) is higher than the predetermined value (for example, over 0°C).
  • a value of the pressure sensor is used to give priority to stability of the cycle, and a stable heating capacity can be ensured to eliminate abnormal stop of the system.
  • a target COP can be obtained by the high-pressure F/B pressure reducing valve control that uses a value of the temperature sensor.
  • a pressure sensor (10) is provided between a refrigerant flow downstream side of the radiator (2) and the pressure reducing means (3, 30), or on a refrigerant flow upstream side of the radiator (2), to detect the refrigerant pressure on the high-pressure side.
  • a cycle stability relative to a variation in the heat pump cycle, which is caused by external factors, can be improved by using the pressure sensor (10) having a good response as means that detects high pressures.
  • a heat pump type water heater includes: a compressor (1) that sucks and compresses refrigerant; a radiator (2) constructed such that heat exchange is performed between refrigerant discharged from the compressor (1) and water for hot-water supply and a flow of refrigerant and a flow of water for hot-water supply are opposed to each other; pressure reducing means (3, 30) that reduces pressure of refrigerant flowing from the radiator (2); and an evaporator (4), in which refrigerant flowing from the pressure reducing means (3, 30) is evaporated and from which refrigerant flows toward a suction side of the compressor (1).
  • a refrigerant pressure on a high-pressure side is controlled such that when the refrigerant pressure on the high-pressure side is less than a predetermined pressure, an actual temperature difference ( ⁇ T) between a refrigerant temperature flowing from the radiator (2) and a water temperature flowing into the radiator (2) becomes a predetermined target temperature difference ( ⁇ Tt).
  • the heater pump type water heater is characterized in that: a discharge temperature sensor (8) for detecting a discharge temperature of refrigerant discharged from the compressor (1) is provided; and at least at the time of starting of the heat pump cycle, a target discharge temperature (Tt) of refrigerant discharged from the compressor (1) is set, a temperature difference ( ⁇ T2) between the target discharge temperature (Tt) and an actual discharge temperature (T) is calculated, and the target discharge temperature (Tt) is corrected to make the temperature difference ( ⁇ T2) equal to or less than a predetermined value.
  • a discharge temperature sensor (8) for detecting a discharge temperature of refrigerant discharged from the compressor (1) is provided; and at least at the time of starting of the heat pump cycle, a target discharge temperature (Tt) of refrigerant discharged from the compressor (1) is set, a temperature difference ( ⁇ T2) between the target discharge temperature (Tt) and an actual discharge temperature (T) is calculated, and the target discharge temperature (Tt) is corrected to make the temperature difference ( ⁇ T2) equal to or
  • a refrigerant state on the high-pressure side can be detected by the use of the temperature sensor (8), which involves less dispersion in detection values as compared with the pressure sensor (10). Therefore, it becomes possible to further surely obtain the target COP.
  • a control of correcting the target discharge temperature (Tt) to make the temperature difference ( ⁇ T2) between the target discharge temperature (Tt) and the actual discharge temperature (T) equal to or less than a predetermined value is performed when at least one of an outside air temperature, an inlet refrigerant temperature of the evaporator (4), and an outlet refrigerant temperature of the evaporator (4) is less than a predetermined value.
  • a value of the pressure sensor is used to give priority to stability of the cycle, a stable heating capacity can be ensured to eliminate abnormal stop of the system.
  • the target COP can be obtained by the high-pressure F/B pressure reducing valve control that uses a value of the temperature sensor.
  • Fig. 1 is a schematic view showing the construction of a heat pump type water heater according to the first embodiment of the invention.
  • the heat pump type water heater according to the embodiment includes a hot-water storage tank 6 that stores water for hot-water supply, water flowing pipes C, H connected to the hot-water storage tank 6, a water pump 7 that circulates water for hot-water supply to the water flowing pipes C, H, a heat pump unit HU of a supercritical heat-pump cycle, described later, which makes a heating means for water for hot-water supply, a control device 16 that controls an operation of the heat pump type water heater, and the like.
  • the hot-water storage tank 6 is formed from a metal (for example, stainless steel) having an excellent corrosion resistance and structured in thermal insulation to be able to keep high-temperature water for hot-water supply warm over a long time.
  • the water for hot-water supply stored in the hot-water storage tank 6 mixes with cold water in use to be adjusted to temperature and then used in a kitchen and a bath, however, can also be made use of as a heat source for floor heating, indoor air conditioning, or the like in addition to hot-water supply.
  • the water flowing pipes C, H includes a cold-water pipe C and a hot-water pipe H, which connect the hot-water storage tank 6 and a water heat exchanger (radiator) 2 described later.
  • the cold-water pipe C is connected at one end thereof to a cold-water outlet 6a provided at a lower portion of the hot-water storage tank 6 and at the other end thereof to an inlet of a water passage (not shown) provided in the water heat exchanger 2.
  • the hot-water pipe H is connected at one end thereof to an outlet of the water passage (not shown) provided in the water heat exchanger 2 and at the other end thereof to a hot-water inlet 6b provided on an upper portion of the hot-water storage tank 6.
  • the water pump 7 produces a water flow so that water for hot-water supply stored in the hot-water storage tank 6 flows from the cold-water outlet 6a to pass through the cold-water pipe C ⁇ the water passage of the water heat exchanger ⁇ the hot-water pipe H, and to return to the hot-water storage tank 6 through the hot-water inlet 6b, as indicated by arrows in Fig. 1.
  • the water pump 7 can adjust an amount of water based on a rotating speed of a motor mounted therein (not shown), and is controlled in electrification by the control device 16.
  • the supercritical heat-pump cycle includes, as shown in Fig. 1, a compressor 1, the water heat exchanger 2, a variable expansion valve 3 as a pressure reducing means, an air heat exchanger (evaporator) 4, an accumulator 5, a refrigerant piping (a high-pressure piping Hi and a low-pressure piping Lo) for connection of these equipments, and the like, and is filled with carbon dioxide (abbreviated below to CO2), which serves as a refrigerant having a low critical temperature.
  • CO2 carbon dioxide
  • the compressor 1 is driven by a motor mounted therein (not shown).
  • the compressor 1 compresses a drawn gas refrigerant to a critical pressure or higher and discharges the compressed refrigerant.
  • An amount of the refrigerant discharged from the compressor 1 is variable according to the rotating speed of the motor.
  • the water heat exchanger 2 performs heat exchange between a gas refrigerant having a high temperature and high pressure pressurized in the compressor 1 and water for hot-water supply fed from the hot-water storage tank 6.
  • the water heat exchanger 2 is provided with a refrigerant passage, which is adjacent to the water passage described above (not shown), and is constructed such that a direction, in which refrigerant flows through the refrigerant passage, and a direction, in which water for hot-water supply flows through the water passage, are opposed to each other.
  • variable expansion valve 3 is provided between the water heat exchanger 2 and the air heat exchanger 4 to reduce pressure of the refrigerant cooled by the water heat exchanger 2 to feed the reduced refrigerant to the air heat exchanger 4.
  • the variable expansion valve 3 is constructed to be electrically adjustable in valve opening degree, and controlled in electrification by the control device 16.
  • the air heat exchanger 4 receives air blown by an outside air fan 4a so that refrigerant, pressure of which is reduced by the variable expansion valve 3, is evaporated by heat exchange with outside air.
  • the accumulator 5 performs vapor-liquid separation of the refrigerant evaporated in the air heat exchanger 4 so that a surplus refrigerant in the cycle is stored therein and only gas refrigerant is drawn into the compressor 1.
  • the reference numeral 8 denotes a discharge temperature sensor that detects a discharge temperature of the refrigerant discharged from the compressor 1
  • the reference numeral 9 denotes an outlet refrigerant temperature sensor that detects a temperature of the refrigerant flowing out from the water heat exchanger 2.
  • the reference numeral 10 denotes a pressure sensor provided on an inlet side or an outlet side of the water heat exchanger 2 to detect a high pressure of the high-pressure piping Hi.
  • the reference numeral 11 denotes a refrigerant temperature sensor at an inlet of the air heat exchanger 4, and the reference numeral 12 denotes a refrigerant temperature sensor at an outlet of the air heat exchanger 4.
  • the reference numeral 13 denotes an outside air temperature sensor that detects an outside air temperature.
  • the reference numeral 14 denotes a water temperature sensor that detects an inlet temperature of water flowing into the water heat exchanger 2, and the reference numeral 15 denotes a boiling-up temperature sensor that detects a temperature of heated water for hot-water supply. All signals detected by a group of these sensors 8 to 15 are input into the control device 16, and electric control of the compressor 1, the variable expansion valve 3, the outside air fan 4a, the water pump 7, etc. is performed according to a flowchart described later.
  • the refrigerant is pressurized by the compressor 1 to become a high-temperature and high-pressure refrigerant, and radiates heat to water for hot-water supply in the water heat exchanger 2 to be cooled.
  • the refrigerant from the water heat exchanger 2 is decompressed in the variable expansion valve 3 based on an opening degree of the variable expansion valve 3.
  • the refrigerant having a low temperature and low pressure decompressed in the variable expansion valve 3 absorbs heat from outside air in the air heat exchanger 4 (the outside air fan 4a: operated) to be evaporated, and is separated into gas refrigerant and liquid refrigerant in the accumulator 5. Thereafter, only the separated gas refrigerant is drawn into the compressor 1, so as to repeat a cycle operation.
  • the water for hot-water supply is pressurized by the water pump 7, absorbs heat from the refrigerant in the water heat exchanger 2 to become a hot water, and is fed to the hot-water storage tank 6 to be stored therein.
  • hot-water temperature is detected by the boiling-up temperature sensor 15, a circulating flow rate is adjusted by the water pump 7, and water temperature control is performed.
  • the water temperature sensor 14 detects a state in which all the water in the hot-water storage tank 6 becomes a hot water and water supplied from the cold-water pipe C becomes high in temperature, the circulation of the refrigerant and the circulation of water for hot-water supply are stopped.
  • Fig. 2 is a flowchart illustrating an example of control performed by the control device 16 in the embodiment of Fig. 1.
  • Fig. 3 is a graph illustrating an example of control characteristics of a high-pressure F/B pressure reducing valve control in the flowchart in Fig. 2
  • Fig. 4 is a graph illustrating an example of correction characteristics of high pressure correction in the flowchart in Fig. 2.
  • the heat pump type water heater 1 makes substantially a system, in which a target high pressure Pt is first provisionally set at the time of starting of a heat pump, a control is performed by the variable expansion valve 3 to provide for a target high pressure Pt while high pressure is detected by the pressure sensor 10, an actual temperature difference ⁇ T between an inlet water temperature and an outlet refrigerant temperature of the water heat exchanger 2 is detected, and the set target high pressure Pt is corrected to a value for obtaining a target COP (i.e., an optimum value, at which COP becomes highest, in the embodiment).
  • a target high pressure Pt is first provisionally set at the time of starting of a heat pump
  • a control is performed by the variable expansion valve 3 to provide for a target high pressure Pt while high pressure is detected by the pressure sensor 10
  • an actual temperature difference ⁇ T between an inlet water temperature and an outlet refrigerant temperature of the water heat exchanger 2 is detected, and the set target high pressure Pt is corrected to a value for obtaining a target
  • Fig. 3 illustrates an example of control characteristics of the variable expansion valve 3.
  • the expansion valve 3 is throttled when an actual high pressure is low relative to a target high pressure, and the expansion valve 3 is opened when an actual high pressure is high relative to a target high pressure. As the actual high pressure approaches the target high pressure, the expansion valve 3 is reduced in opening degree to improve the heat-pump cycle in stability.
  • step S3 it is determined whether the target high pressure has been reached.
  • a high-pressure F/B pressure reducing valve control in step S2 is continued.
  • the procedure proceeds to step S4 and an actual temperature difference ⁇ T between an inlet water temperature and an outlet refrigerant temperature of the water heat exchanger 2 is detected.
  • step S5 a temperature difference ⁇ T1 between a target temperature difference ⁇ Tt for obtaining an optimum COP, and the actual temperature difference ⁇ T is calculated.
  • the target temperature difference ⁇ Tt may be a predetermined value (for example, 10 °C), or may be calculated according to the map.
  • step S6 it is determined whether an absolute value of the temperature difference ⁇ T1 calculated in step S5 is equal to or less than a predetermined value (3 °C in this example).
  • a predetermined value 3 °C in this example.
  • the procedure proceeds to step S7 to correct the target high pressure Pt and repeats again the high-pressure F/B pressure reducing valve control in step S2.
  • Fig. 4 illustrates an example of correction characteristics of high-pressure correction.
  • the temperature difference ⁇ T1 calculated in step S5 is positive (an actual temperature difference ⁇ T is short of the target temperature difference ⁇ Tt)
  • the target high pressure Pt is positive-corrected.
  • the temperature difference is negative (an actual temperature difference ⁇ T is over the target temperature difference ⁇ Tt)
  • the target high pressure Pt is negative-corrected.
  • step S9 it is determined whether an operation shutdown command has been input. When the determination of step S9 is NO and any operation shutdown command is not input, the optimum high-pressure F/B pressure reducing valve control in step S8 is continued. Thereafter, when an operation shutdown command is input and results of the determination in step S9 is YES, the boiling-up operation is ended.
  • a target high pressure Pt on a high-pressure side is set, and a refrigerant pressure on the high-pressure side is controlled so as to become the target high pressure Pt. Furthermore, the temperature difference ⁇ T1 between the target temperature difference ⁇ Tt and the actual temperature difference ⁇ T is calculated, and the target high pressure Pt is corrected so as to make the temperature difference ⁇ T1 equal to or less than a predetermined value.
  • the pressure sensor involves a large dispersion in detection values and it is difficult to obtain a target COP.
  • the target COP can be obtained by correcting the target high pressure Pt on the basis of an actual temperature difference ⁇ T detected by the temperature sensor, which involves less dispersion. Since control of the pressure reducing valve is made possible even when either of the pressure sensor and the temperature sensor is abnormal, reliability of the system can be improved on a user's side.
  • Fig. 5 is a flowchart illustrating an example of control performed by the control device 16 in the second embodiment.
  • Fig. 6 illustrates an example of a map for calculation of a target discharge temperature Tt in the flowchart of Fig. 5, and
  • Fig. 7 shows a graph illustrating an example of correction characteristics of high-pressure correction in the flowchart of Fig. 5.
  • a heat pump type water heater is the same in construction as that in the first embodiment.
  • a target high pressure Pt is corrected while performing a high-pressure F/B pressure reducing valve control on the basis of a temperature difference in the same manner as in the first embodiment.
  • the temperature difference is calculated by the use of a discharge temperature of the refrigerant discharged from the compressor 1.
  • step S12 respective cycle functional parts such as the compressor 1, the outside air fan 4a, the water pump 7, etc. are operated. Furthermore, while an actual pressure is detected by the pressure sensor 10, an opening degree of the variable expansion valve 3 is controlled (i.e., high-pressure F/B pressure reducing valve control) so as to obtain the target high pressure Pt.
  • Fig. 3 illustrates an example of control characteristics of the variable expansion valve 3. In the characteristics, the expansion valve 3 is throttled when an actual high pressure is low relative to a target high pressure, and the expansion valve 3 is opened when an actual pressure is high relative to a target high pressure. As an actual high pressure approximates to the target high pressure, the expansion valve is reduced in opening degree to improve the stability of the heat-pump cycle.
  • step S13 it is determined whether the target high pressure has been reached.
  • the high-pressure F/B pressure reducing valve control in step S12 is continued.
  • the procedure proceeds to step S14 and a target discharge temperature Tt is calculated from an outside air temperature and a target boiling-up temperature based on the map (or calculating formula) in Fig. 6.
  • step S15 a temperature difference ⁇ T2 between the target discharge temperature Tt for obtaining an optimum COP, and an actual discharge temperature T is calculated.
  • step S16 it is determined whether an absolute value of the temperature difference ⁇ T2 calculated in step S15 is equal to or less than a predetermined value (3°C in this example).
  • a predetermined value 3°C in this example.
  • the procedure proceeds to step S17 to correct the target high pressure Pt and repeats again the high-pressure F/B pressure reducing valve control in step S12.
  • Fig. 7 illustrates an example of correction characteristics of high-pressure correction. In the characteristics of Fig. 7, when the temperature difference ⁇ T2 calculated in step S15 is positive (an actual discharge temperature T is short of the target discharge temperature Tt), the target high pressure Pt is positive-corrected. Furthermore, when the temperature difference ⁇ T2 is negative (an actual discharge temperature T is over the target discharge temperature Tt), the target high pressure Pt is negative-corrected.
  • step S19 it is determined whether an operation shutdown command has been input. When the determination of step S19 is NO and any operation shutdown command is not input, the optimum high-pressure F/B pressure reducing valve control in step S18 is continued. In contrast, when an operation shutdown command is input and the determination of step S19 is YES, the boiling-up operation is ended.
  • the target high pressure Pt on a high-pressure side is set, the refrigerant pressure on the high-pressure side is controlled so as to become the target high pressure Pt, the target discharge temperature Tt of the refrigerant discharged from the compressor 1 is set, the temperature difference ⁇ T2 between the target discharge temperature Tt and an actual discharge temperature T is calculated, and the target high pressure Pt is corrected so as to make the temperature difference ⁇ T2 equal to or less than a predetermined value.
  • the pressure sensor involves a large dispersion in detection values, it is difficult to obtain a target COP.
  • the target COP can be obtained by correcting the target high pressure Pt on the basis of an actual discharge temperature T detected by the temperature sensor, which involves less dispersion. Since control of the pressure reducing valve 3 is made possible even when either of the pressure sensor and the temperature sensor is abnormal, reliability of the system can be improved on a user's side.
  • Fig. 8 is a flowchart illustrating an example of control performed by the control device 16 in the third embodiment of the invention.
  • the invention provides a system, in which a high-pressure F/B pressure reducing valve control and a temperature difference F/B pressure reducing valve control are switched based on an outside air temperature detected by the outside air temperature sensor 13.
  • step S21 it is determined whether the outside air temperature is equal to or higher than a predetermined value (0°C in the embodiment).
  • the procedure proceeds to step S22 to set a target temperature difference ⁇ Tt for obtaining an optimum COP.
  • step S23 an actual temperature difference ⁇ T between an inlet water temperature and an outlet refrigerant temperature of the water heat exchanger 2 is detected, and the temperature difference F/B pressure reducing valve control for control of the variable expansion valve 3 is performed so as to obtain a target temperature difference ⁇ Tt.
  • Fig. 9 is a graph illustrating an example of control characteristics of the temperature difference F/B pressure reducing valve control in the flowchart in Fig. 8. In the characteristics, when a temperature difference ⁇ T1 is positive (an actual temperature difference ⁇ T is short of the target temperature difference ⁇ Tt), the expansion valve 3 is throttled. In contrast, when the temperature difference is negative (an actual temperature difference AT is over the target temperature difference ⁇ Tt), the expansion valve 3 is opened.
  • the target temperature difference ⁇ Tt may be a predetermined value (for example, 10°C), or may be calculated according to the map.
  • the high-pressure F/B pressure reducing valve control is performed such that the determination in step S21 is NO and an outside air temperature is lower than 0°C, the procedure proceeds to step S24 to first set a target high pressure Pt provisionally. Then, control operation is performed in the next step S25 by the variable expansion valve 3 so as to obtain the target high pressure Pt while detecting a high pressure by means of the pressure sensor 10. Furthermore, an actual temperature difference ⁇ T between an inlet water temperature and an outlet refrigerant temperature of the water heat exchanger 2 is detected, and the target high pressure Pt thus set is corrected to an optimum value, at which COP becomes highest.
  • the target high pressure Pt is set, the refrigerant pressure on the high-pressure side is controlled so as to become the target high pressure Pt, and a temperature difference ⁇ T1 between the target temperature difference ⁇ Tt and an actual temperature difference ⁇ T is calculated. Furthermore, control operation that corrects the target high pressure Pt so as to make the temperature difference ⁇ T1 equal to or less than a predetermined value is performed, in the case where at least one of the outside air temperature, the inlet refrigerant temperature of the air heat exchanger 4, and the outlet refrigerant temperature of the air heat exchanger 4 is less than the predetermined value.
  • stability of the cycle can be improved by performing the high-pressure F/B pressure reducing valve control with the use of the pressure sensor at the time of low temperature when at least one of the outside air temperature, the inlet refrigerant temperature of the air heat exchanger 4, and the outlet refrigerant temperature of the air heat exchanger 4 is less than a predetermined value (for example, 0°C or lower).
  • the boiling-up operation is performed by the high-pressure F/B pressure reducing valve control corresponding to a target COP, in a high temperature state where at least one of the outside air temperature, the inlet refrigerant temperature of the air heat exchanger 4, and the outlet refrigerant temperature of the air heat exchanger 4 is higher than the predetermined value (for example, over 0°C).
  • a value of the pressure sensor is used to give priority to stability of the cycle, and a stable heating capacity can be ensured to eliminate abnormal stop of the system. Furthermore, at the time of a high outside air temperature, a target COP can be obtained by the high-pressure F/B pressure reducing valve control that uses a value of the temperature sensor.
  • Fig. 10 is a flowchart illustrating an example of control performed by the control device 16 in the fourth embodiment of the invention.
  • the invention provides a system, in which a high-pressure F/B pressure reducing valve control and a discharge-temperature difference F/B pressure reducing valve control are switched over according to the outside air temperature detected by the outside air temperature sensor 13.
  • step S31 it is determined whether an outside air temperature is equal to or higher than a predetermined value (0°C in the embodiment).
  • the procedure proceeds to step S32 to set a target discharge temperature Tt for obtaining an optimum COP.
  • step S33 an actual discharge temperature T of the compressor 1 is detected, and the discharge-temperature difference F/B pressure reducing valve control for control of the variable expansion valve 3 is performed so as to obtain a target discharge temperature Tt.
  • Fig. 11 is a graph illustrating an example of control characteristics of the discharge-temperature difference F/B pressure reducing valve control in the flowchart in Fig. 10. In the characteristics, when a temperature difference ⁇ T2 is positive (an actual discharge temperature T is short of the target discharge temperature Tt), the expansion valve 3 is throttled. In contrast, when the temperature difference is negative (an actual discharge temperature T is over the target discharge temperature Tt), the expansion valve 3 is opened.
  • the high-pressure F/B pressure reducing valve control is performed such that when the determination in step S31 is NO and the outside air temperature is lower than 0°C, the procedure proceeds to step S34 to first set a target high pressure Pt provisionally. Furthermore, the control is performed in the next step S35 by the variable expansion valve 3 so as to obtain the target high pressure Pt while detecting a high pressure by means of the pressure sensor 10. In addition, the actual temperature difference ⁇ T between the inlet water temperature and the outlet refrigerant temperature of the water heat exchanger 2 is detected, and the target high pressure Pt thus set is corrected to an optimum value, at which COP becomes highest.
  • a target high pressure Pt is set, a refrigerant pressure on a high-pressure side is controlled so as to become the target high pressure Pt, and a target discharge temperature Tt of the refrigerant discharged from the compressor 1 is set. Furthermore, the temperature difference ⁇ T2 between the target discharge temperature Tt and an actual discharge temperature T is calculated.
  • a control that corrects the target high pressure Pt so as to make the temperature difference ⁇ T2 equal to or less than a predetermined value is performed, in the case where at least one of the outside air temperature, the inlet refrigerant temperature of the air heat exchanger 4, and the outlet refrigerant temperature of the air heat exchanger 4 is less than a predetermined value.
  • a target COP can be obtained by the high-pressure F/B pressure reducing valve control that uses a value of the temperature sensor at the time of high outside air temperature.
  • Fig. 12 is a schematic view showing a structure of a heat pump type water heater according to another embodiment of the invention.
  • the variable expansion valve 3 is used as a pressure reducing means in the above embodiments.
  • the invention is not limited to the embodiments but a heat pump cycle, in which an ejector 30 is used as the pressure reducing means, will be used as shown in Fig. 12. Even in this case, the same effect can be obtained.
  • the target high pressure Pt on the high-pressure side is set at the time of starting of the heat pump cycle.
  • the same effect can also be obtained by performing a control, in which a target discharge temperature Tt of a refrigerant discharged from the compressor 1 is set in place of the target high pressure Pt on the high-pressure side, and a target temperature difference Tt is corrected so that a temperature difference ⁇ T2 between the target discharge temperature Tt and an actual discharge temperature T becomes equal to or less than a predetermined value.
EP05765649A 2004-07-12 2005-07-12 Dispositif d'alimentation en eau chaude de type pompe à chaleur Withdrawn EP1777471A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004204956 2004-07-12
PCT/JP2005/012800 WO2006006578A1 (fr) 2004-07-12 2005-07-12 Dispositif d’alimentation en eau chaude de type pompe à chaleur

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EP1777471A1 true EP1777471A1 (fr) 2007-04-25

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WO (1) WO2006006578A1 (fr)

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CN102022871A (zh) * 2010-12-09 2011-04-20 东莞市泰格冷热设备有限公司 一种冷热一体机恒温控制装置
WO2010093509A3 (fr) * 2009-02-13 2011-12-29 General Electric Company Commande de chauffe-eau pompe à chaleur
CN102425872A (zh) * 2007-11-30 2012-04-25 三菱电机株式会社 冷冻循环装置
US8422870B2 (en) 2009-02-13 2013-04-16 General Electric Company Residential heat pump water heater
CN103884104A (zh) * 2012-12-21 2014-06-25 珠海格力电器股份有限公司 一种基于热泵热水器的控制方法、装置、控制器和系统
EP2610558A3 (fr) * 2011-12-29 2015-10-14 Mitsubishi Electric Corporation Pompe à chaleur et procédé de commande d'une pompe à chaleur
US9206996B2 (en) 2014-01-06 2015-12-08 General Electric Company Water heater appliance
JP2021165609A (ja) * 2020-04-07 2021-10-14 日立グローバルライフソリューションズ株式会社 ヒートポンプ式給湯機

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JP5055884B2 (ja) * 2006-08-03 2012-10-24 ダイキン工業株式会社 空気調和装置
JP5879783B2 (ja) * 2011-07-11 2016-03-08 セイコーエプソン株式会社 検出装置
JP5797998B2 (ja) * 2011-10-13 2015-10-21 株式会社コロナ ヒートポンプ式給湯装置
JP5761016B2 (ja) * 2011-12-28 2015-08-12 ダイキン工業株式会社 ヒートポンプ式給湯機
JP5843642B2 (ja) * 2012-02-08 2016-01-13 日立アプライアンス株式会社 ヒートポンプ式液体加熱装置
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JP5861577B2 (ja) * 2012-07-05 2016-02-16 株式会社デンソー 給湯装置
JP2020079649A (ja) * 2017-02-21 2020-05-28 株式会社前川製作所 ヒートポンプ装置の制御方法及びヒートポンプ装置

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JP3740380B2 (ja) * 2000-04-19 2006-02-01 株式会社デンソー ヒートポンプ式給湯器
JP3807930B2 (ja) * 2000-12-01 2006-08-09 株式会社デンソー 給湯装置

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CN102425872A (zh) * 2007-11-30 2012-04-25 三菱电机株式会社 冷冻循环装置
CN102425872B (zh) * 2007-11-30 2014-06-25 三菱电机株式会社 冷冻循环装置
WO2010093509A3 (fr) * 2009-02-13 2011-12-29 General Electric Company Commande de chauffe-eau pompe à chaleur
US8422870B2 (en) 2009-02-13 2013-04-16 General Electric Company Residential heat pump water heater
US9845978B2 (en) 2009-02-13 2017-12-19 Haier Us Appliance Solutions, Inc. Residential heat pump water heater
CN102022871A (zh) * 2010-12-09 2011-04-20 东莞市泰格冷热设备有限公司 一种冷热一体机恒温控制装置
EP2610558A3 (fr) * 2011-12-29 2015-10-14 Mitsubishi Electric Corporation Pompe à chaleur et procédé de commande d'une pompe à chaleur
CN103884104A (zh) * 2012-12-21 2014-06-25 珠海格力电器股份有限公司 一种基于热泵热水器的控制方法、装置、控制器和系统
CN103884104B (zh) * 2012-12-21 2016-08-24 珠海格力电器股份有限公司 一种基于热泵热水器的控制方法、装置、控制器和系统
US9206996B2 (en) 2014-01-06 2015-12-08 General Electric Company Water heater appliance
JP2021165609A (ja) * 2020-04-07 2021-10-14 日立グローバルライフソリューションズ株式会社 ヒートポンプ式給湯機
JP7174732B2 (ja) 2020-04-07 2022-11-17 日立グローバルライフソリューションズ株式会社 ヒートポンプ式給湯機

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