WO2006006578A1 - 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
WO2006006578A1
WO2006006578A1 PCT/JP2005/012800 JP2005012800W WO2006006578A1 WO 2006006578 A1 WO2006006578 A1 WO 2006006578A1 JP 2005012800 W JP2005012800 W JP 2005012800W WO 2006006578 A1 WO2006006578 A1 WO 2006006578A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
pressure
temperature
target
heat pump
Prior art date
Application number
PCT/JP2005/012800
Other languages
English (en)
Japanese (ja)
Inventor
Jouji Kuroki
Hisayoshi Sakakibara
Teruhiko Taira
Susumu Kawamura
Masato Murayama
Original Assignee
Denso Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corporation filed Critical Denso Corporation
Priority to JP2006529048A priority Critical patent/JP4337880B2/ja
Priority to EP05765649A priority patent/EP1777471A1/fr
Publication of WO2006006578A1 publication Critical patent/WO2006006578A1/fr

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Classifications

    • 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 means for heating hot water, and more particularly to a method for controlling a pressure reducing means during a boiling operation.
  • the present invention has been made in view of the above-described conventional problems, and an object of the present invention is to provide a heat pump type water heater having high cycle stability against external factors. Disclosure of the invention
  • the present invention employs the technical means described in claims 1 to 4. That is, in the invention described in claim 1, the hot water heater for heating hot water in a vapor compression heat pump cycle that moves the heat on the low temperature side to the high temperature side, the compressor (1) for sucking and compressing the refrigerant Heat exchange between the refrigerant discharged from the compressor (1) and the hot water supply water, and the radiator (2) configured so that the refrigerant flow and the hot water supply flow face each other, and outflow from the radiator (2) Pressure reducing means (3, 30) and pressure reducing means (3, 30) force to evaporate the flowing refrigerant and absorb the heat, and at the suction side of the compressor (1) When the refrigerant pressure on the high-pressure side is lower than the predetermined pressure, the refrigerant flowing out of the radiator (2) and the hot water supply water flowing into the radiator (2) The heat pump type water heater that controls the refrigerant pressure on the high-pressure side so that the actual temperature difference ( ⁇ T) becomes the predetermined target temperature difference ( ⁇ Tt),
  • the target pressure (Pt) on the high pressure side is set, the refrigerant pressure on the high pressure side is controlled so as to be the target pressure (Pt), and the target temperature difference ( ⁇ ⁇ and actual temperature difference ( ⁇ T ), And the target pressure (Pt) is corrected so that the temperature difference ( ⁇ T1) is less than or equal to a predetermined value.
  • the target is determined based on the actual temperature difference ( ⁇ ⁇ ⁇ ) detected from a temperature sensor with little variation.
  • Pt the pressure
  • the pressure reducing valve can be controlled even when either the pressure sensor or the temperature sensor is abnormal, the reliability of the system for the user can be improved.
  • the hot water heater for heating the hot water supply in a vapor compression heat pump cycle that moves the heat on the low temperature side to the high temperature side, the compressor sucking and compressing the refrigerant (1) and a radiator (2) configured to exchange heat between the refrigerant discharged from the compressor (1) and the hot water supply water, and the refrigerant flow and the hot water supply flow are opposed to each other.
  • the refrigerant pressure on the high-pressure side is less than a predetermined pressure
  • the refrigerant flowing out of the radiator (2) and the hot water supply water flowing into the radiator (2) Heat pump that controls the refrigerant pressure on the high-pressure side so that the actual temperature difference ( ⁇ T) of the target becomes the predetermined target temperature difference ( ⁇ )
  • ⁇ T actual temperature difference
  • ⁇ predetermined target temperature difference
  • the refrigerant pressure on the high-pressure side is controlled so that it becomes the pressure (Pt), and the target discharge temperature (Tt) of the refrigerant discharged from the compressor (1) is set, and the target discharge temperature (Tt) and the actual discharge temperature (T ) Is calculated, and the target pressure (Pt) is corrected so that the temperature difference ( ⁇ ⁇ 2) is less than or equal to a predetermined value.
  • the target pressure is determined from the actual discharge temperature (T) detected by a temperature sensor with little variation. It is possible to achieve the target COP by correcting (Pt).
  • the pressure reducing valve can be controlled even when either the pressure sensor or the temperature sensor is abnormal, the reliability of the system for the user can be improved.
  • the target pressure (Pt) is set, the refrigerant pressure on the high pressure side is controlled so as to be the target pressure (Pt), and the target temperature difference ( ⁇ ⁇
  • the temperature difference ( ⁇ 1) between the actual temperature difference ( ⁇ ) and the target pressure (Pt) is corrected so that the temperature difference ( ⁇ 1) is less than the specified value. It is characterized in that it is performed when at least four of the inlet refrigerant temperature of (4) and the outlet refrigerant temperature of the evaporator (4) are lower than a predetermined value.
  • 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 more than a predetermined value.
  • cycle stability can be improved by performing high-pressure FZB pressure reducing valve control using a pressure sensor.
  • the outside air temperature, the inlet of the evaporator (4) When at least four of the refrigerant temperature and the outlet refrigerant temperature of the evaporator (4) are higher than the specified value or high (for example, over 0 ° C), the high-pressure FZB pressure-reducing valve according to the target COP Boiling operation is performed by control.
  • the target pressure (Pt) is set, the refrigerant pressure on the high-pressure side is controlled so as to be the target pressure (Pt), and the compressor (1) Set the target discharge temperature (Tt) of the refrigerant to be discharged, calculate the temperature difference ( ⁇ 2) between the target discharge temperature (Tt) and the actual discharge temperature (T), and the temperature difference ( ⁇ 2) is less than the predetermined value
  • the control to correct the target pressure (Pt) is performed 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. It is characterized by that.
  • the temperature sensor such as a thermistor has a temperature detection delay due to the heat capacity of the functional parts and heat pump cycle, and the pressure reducing means (3, It may be difficult to control 30) in real time, and it is necessary to ensure stability against fluctuations in the heat pump cycle.
  • 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 more than a predetermined value.
  • cycle stability can be improved by performing high-pressure FZB pressure reducing valve control using a pressure sensor.
  • at least four of the outside air temperature, the refrigerant temperature at the inlet of the evaporator (4), and the refrigerant temperature at the outlet of the evaporator (4) are higher than a predetermined value or high (for example, exceeding 0 ° C).
  • the boiling operation is performed by controlling the high pressure FZB pressure reducing valve according to the target COP.
  • the compressor (1) for sucking and compressing the refrigerant force exchange heat between the refrigerant discharged and the hot water supply water, and the refrigerant flow and the hot water supply water.
  • a radiator (2) configured to face the flow, a decompression means (3, 30) for decompressing the refrigerant flowing out of the radiator (2), and a refrigerant flowing out of the decompression means (3, 30)
  • an evaporator (4) that flows out the refrigerant toward the suction side of the compressor (1), and flows out of the radiator (2) when the refrigerant pressure on the high-pressure side is lower than a predetermined pressure.
  • It has a discharge temperature sensor (8) that detects the discharge temperature of the refrigerant discharged from the compressor (1), and at least when the heat pump cycle starts, the target discharge temperature (Tt) of the refrigerant discharged from the compressor (1) Set and calculate the temperature difference ( ⁇ ⁇ 2) between the target discharge temperature (Tt) and the actual discharge temperature (T), and correct the target discharge temperature (Tt) so that the temperature difference ( ⁇ ⁇ 2) is less than the specified value. It is characterized by this.
  • the target discharge temperature (Tt) is corrected so that the temperature difference ( ⁇ T2) between the target discharge temperature (Tt) and the actual discharge temperature (T) is equal to or less than a predetermined value.
  • This control is performed when at least four of the outside air temperature, the inlet refrigerant temperature of the evaporator (4), and the outlet refrigerant temperature of the evaporator (4) are lower than a predetermined value.
  • FIG. 1 is a schematic diagram showing a configuration of a heat pump type water heater in a first embodiment of the present invention.
  • FIG. 2 is a flowchart showing a control example of the control device 16 in the embodiment of FIG.
  • FIG. 3 is a graph showing an example of control characteristics of high-pressure F / B pressure reducing valve control in the flowchart of FIG.
  • FIG. 4 is a graph showing an example of correction characteristics of high-pressure correction in the flowchart of FIG.
  • FIG. 5 is a flowchart showing a control example of the control device 16 in the second embodiment of the present invention.
  • FIG. 6 is an example of a map for calculating a target discharge temperature Tt in the flowchart of FIG.
  • FIG. 7 is a graph showing an example of correction characteristics of high pressure correction in the flowchart of FIG.
  • FIG. 8 is a flowchart showing a control example of the control device 16 in the third embodiment of the present invention.
  • FIG. 9 is a graph showing an example of control characteristics of temperature difference FZB pressure reducing valve control in the flowchart of FIG. 8.
  • FIG. 10 is a flowchart showing a control example of the control device 16 in the fourth embodiment of the present invention.
  • FIG. 11 is a graph showing an example of control characteristics of discharge temperature difference F / B pressure reducing valve control in the flowchart of FIG. 10.
  • FIG. 12 is a schematic diagram showing a configuration of a heat pump type water heater in another embodiment of the present invention.
  • FIG. 1 is a schematic diagram showing the configuration of the heat pump type water heater in the first embodiment of the present invention.
  • the heat pump type water heater in this embodiment has a hot water storage tank 6 for storing hot water supply water, a flowing water pipe C′H connected to the hot water storage tank 6, and a water supply water flowing through the flowing water pipe C′H. It consists of a data pump 7, a heat pump unit HU of a supercritical heat pump cycle, which will be described later, which is a means for heating hot water, and a control device 16 that controls the operation of the heat pump water heater.
  • the hot water storage tank 6 is made of metal (for example, made of stainless steel) excellent in corrosion resistance and has a heat insulating structure, and can keep hot hot water for a long time. Hot water stored in the hot water storage tank 6 is mixed with cold water and adjusted in temperature during use, and is mainly used in kitchens and baths.In addition to hot water, for example, for floor heating or indoor air conditioning It can also be used as a heat source.
  • metal for example, made of stainless steel
  • Hot water stored in the hot water storage tank 6 is mixed with cold water and adjusted in temperature during use, and is mainly used in kitchens and baths.In addition to hot water, for example, for floor heating or indoor air conditioning It can also be used as a heat source.
  • the flowing water pipe C 1 H is composed of a cold water pipe C and a hot water pipe H that connect the hot water storage tank 6 and a hydrothermal exchanger (radiator) 2 described later.
  • One end of the chilled water pipe C is connected to a chilled water outlet 6 a provided in the lower part of the hot water storage tank 6, and the other end is connected to an inlet of a water passage (not shown) provided in the hydrothermal exchanger 2.
  • the hot water pipe H has one end connected to an outlet of a water passage (not shown) provided in the water heat exchanger 2 and the other end connected to a hot water inlet 6b provided in the upper part of the hot water storage tank 6.
  • the hot water in the hot water storage tank 6 flows from the cold water outlet 6a to the cold water pipe C ⁇ water passage ⁇ hot water pipe H and from the hot water inlet 6b to the hot water tank 6 A water flow is generated so as to recirculate.
  • the water pump 7 can adjust the amount of flowing water according to the rotation speed of a motor (not shown) incorporated therein, and is energized and controlled by the control device 16.
  • the supercritical heat pump cycle includes a compressor 1, a water heat exchanger 2, a variable expansion valve 3 as a decompression means, an air heat exchanger (evaporator) 4, an accumulator 5, It consists of refrigerant pipes (high-pressure pipe Hi and low-pressure pipe Lo) that connect these devices, and carbon dioxide (hereinafter abbreviated as C02) refrigerant with a low critical temperature is enclosed as the refrigerant.
  • refrigerant pipes high-pressure pipe Hi and low-pressure pipe Lo
  • C02 carbon dioxide
  • the compressor 1 is driven by a built-in motor (not shown) and receives the sucked gas refrigerant. Compress to discharge above the field pressure and discharge. The refrigerant discharge amount of the compressor 1 varies according to the rotation speed of the motor.
  • the water heat exchanger 2 exchanges heat between the high-temperature and high-pressure gas refrigerant pressurized by the compressor 1 and the hot water supplied from the hot water storage tank 6, and is adjacent to the water passage described above.
  • a refrigerant passage (not shown) is provided, and the flow direction of the refrigerant flowing through the refrigerant passage is opposed to the flow direction of hot water supply water flowing through the water passage.
  • variable expansion valve 3 is provided between the water heat exchanger 2 and the air heat exchanger 4, and the water heat exchanger
  • the refrigerant cooled in 2 is decompressed and supplied to the air heat exchanger 4.
  • the variable expansion valve 3 has a configuration in which the valve opening degree can be electrically adjusted, and is energized and controlled by the control device 16.
  • the air heat exchanger 4 receives air blown by the outside air fan 4a, and evaporates the refrigerant decompressed by the variable expansion valve 3 by heat exchange with the outside air.
  • the accumulator 5 gas-liquid separates the refrigerant evaporated in the air heat exchanger 4 and stores surplus refrigerant in the cycle, and causes the compressor 1 to suck only the gas refrigerant.
  • 8 is a discharge temperature sensor that detects the discharge temperature of the refrigerant discharged from the compressor 1
  • 9 is an outlet refrigerant temperature sensor that detects the temperature of the refrigerant flowing out of the water heat exchanger 2.
  • Reference numeral 10 denotes a pressure sensor which is set on the inlet side or the outlet side of the water heat exchanger 2 and detects the high pressure on the high pressure pipe Hi side.
  • 11 is a refrigerant temperature sensor at the inlet of the air heat exchanger 4, and 12 is a refrigerant temperature sensor at the outlet of the air heat exchanger 4.
  • Reference numeral 13 denotes an outside air temperature sensor that detects the ambient air temperature.
  • Reference numeral 14 denotes a water temperature sensor that detects the temperature of the inlet water flowing into the water heat exchanger 2, and reference numeral 15 denotes a boiling temperature sensor that detects the hot water temperature of the hot water supply water. All signals detected by these sensor groups are input to the control device 16, and the energization control of the compressor 1, the variable expansion valve 3, the outside air fan 4a, the water pump 7, and the like is controlled according to a flowchart and the like described later.
  • the refrigerant is pressurized by the compressor 1 to become high temperature and pressure, dissipates heat to the hot water supply water in the water heat exchanger 2 and is cooled, supplied to the variable expansion valve 3, and according to the opening of the variable expansion valve 3. Depressurized. Depressurized low-temperature low-pressure refrigerant
  • the air heat exchanger 4 (outside air fan 4a: operating) absorbs heat from outside air and evaporates, and after the gas and liquid are separated by the accumulator 5, the cycle in which only the gas refrigerant is sucked into the compressor 1 is repeated.
  • the hot water supply water is pressurized by the water pump 7, absorbs heat from the refrigerant in the water heat exchanger 2 to become hot water, and is sent to the hot water storage tank 6 for storage.
  • the boiling temperature is controlled by detecting the hot water temperature with the boiling temperature sensor 15 and adjusting the circulation flow rate with the water pump 7.
  • the water temperature sensor 14 detects that the hot water storage tank 6 has become hot water and the temperature of the water supply from the cold water pipe C has increased, the circulation of the refrigerant and hot water is stopped.
  • FIG. 2 is a flowchart showing an example of control of the control device 16 in the embodiment of FIG.
  • FIG. 3 is a graph showing an example of control characteristics of high-pressure F / B pressure reducing valve control in the flowchart of FIG. 2, and is a graph showing an example of correction characteristics of high-pressure correction in the flowchart of FIG.
  • the heat pump type hot water heater 1 of the present invention first temporarily sets a target high pressure Pt when the heat pump is started, and detects the high pressure with the pressure sensor 10, while the variable expansion valve 3 detects the target high pressure Pt.
  • the actual temperature difference ⁇ between the inlet water temperature and the outlet refrigerant temperature of the water heat exchanger 2 is detected and set, and the target COP (this implementation) is set. In the form, it is a system that corrects the COP to the highest value).
  • step S1 of Fig. 2 it is determined from the outside air temperature 'water temperature at the inlet of the water heat exchanger 2' target boiling temperature, etc. Estimate the high pressure when the cycle is stabilized and tentatively set the target high pressure Pt.
  • each cycle function product such as compressor 1, outdoor fan 4a, water pump 7, etc. is operated, and the pressure sensor 10 detects the actual pressure to reach the target high pressure Pt.
  • Control the opening of expansion valve 3 (high pressure FZB pressure reducing valve control).
  • FIG. 3 shows an example of control characteristics of the variable expansion valve 3. If the actual high pressure is lower than the target high pressure, the expansion valve is throttled. If the actual high pressure is higher than the target high pressure, the expansion valve is opened. And real height As the pressure approaches the target high pressure, the opening of the expansion valve is reduced to improve the stability of the heat pump cycle.
  • step S3 it is determined whether or not the target high pressure has been reached. If the determination result is NO, the target high pressure has been reached. B Continue pressure reducing valve control. If the target high pressure is reached and the determination result in step S3 is YES, the process proceeds to step S4, and the actual temperature difference ⁇ between the inlet water temperature and the outlet refrigerant temperature of the water heat exchanger 2 is detected. In step S5, the target temperature difference A Tt to achieve the optimum COP and the temperature difference ⁇ 1 between the actual temperature difference ⁇ are calculated. The target temperature difference may be a predetermined value (for example, 10 ° C.) or may be calculated according to a map.
  • step S6 it is determined whether or not the absolute value of the temperature difference ⁇ 1 calculated in step S5 is equal to or less than a predetermined value (3 ° C in this example). If the determination result is NO and the absolute value of the temperature difference ⁇ 1 is greater than or equal to the predetermined value, the process proceeds to step S7, the target high pressure Pt is corrected, and the high pressure F / B pressure reducing valve control in step S2 is repeated. is there.
  • Figure 4 shows an example of correction characteristics for high-pressure correction.
  • step S5 If the temperature difference ⁇ 1 calculated in step S5 is positive (if the actual temperature difference ⁇ is insufficient for the target temperature difference ⁇ Tt), the target high pressure Pt is positively corrected, and if it is negative (the actual temperature difference ⁇ T is the target) When the temperature difference ⁇ Tt is exceeded), the target high pressure Pt is negatively corrected.
  • step S9 it is determined whether or not an operation stop command has been input. If the determination result is NO and no operation stop command is input, the optimum high pressure FZB pressure reducing valve control in step S8 is continued. When the operation stop command is input and the judgment result in step S9 is YES, the above boiling operation is terminated.
  • the target pressure Pt is calculated from the actual temperature difference ⁇ detected by a temperature sensor with little variation. By correcting it, it is possible to achieve the target COP.
  • the pressure reducing valve can be controlled even if it is abnormal, so that the reliability of the system on the user side can be improved.
  • FIG. 5 is a flowchart showing a control example of the control device 16 in the second embodiment of the present invention.
  • FIG. 6 is an example of a map for calculating the target discharge temperature Tt in the flowchart of FIG. 5
  • FIG. 7 is a graph showing an example of correction characteristics of high pressure correction in the flowchart of FIG.
  • the configuration of the heat pump type hot water heater is the same as that of the first embodiment described above.
  • the target pressure Pt is corrected by the temperature difference while performing the high pressure F / B pressure reducing valve control.
  • the difference is that the temperature difference is calculated using the discharge temperature of the refrigerant discharged from machine 1.
  • step S11 of Fig. 5 it is determined from the outside air temperature 'the inlet water temperature of the water heat exchanger 2' the target boiling temperature, etc. Estimate the high pressure when the cycle is stabilized and tentatively set the target high pressure Pt.
  • each cycle function product such as compressor 1, outside air fan 4a, water pump 7, etc. is operated and variable while detecting the actual pressure with pressure sensor 10 so as to reach the target high pressure Pt.
  • Controls the opening of the expansion valve 3 (high pressure FZB pressure reducing valve control).
  • FIG. 3 shows an example of control characteristics of the variable expansion valve 3. If the actual high pressure is lower than the target high pressure, the expansion valve is throttled. If the actual high pressure is higher than the target high pressure, the expansion valve is opened. As the actual high pressure approaches the target high pressure, the opening degree of the expansion valve is decreased to improve the stability of the heat pump cycle.
  • the next step S13 it is determined whether or not the target high pressure has been reached.
  • step S13 the target discharge temperature Tt is calculated from the outside air temperature and the target boiling temperature according to the map in Fig. 6 or the calculation formula). Is calculated.
  • step S15 a temperature difference ⁇ 2 between the target discharge temperature Tt and the actual discharge temperature T for achieving the optimum COP is calculated.
  • step S16 it is determined whether or not the absolute value of the temperature difference ⁇ 2 calculated in step S15 is equal to or less than a predetermined value (3 ° C. in this example). If the determination result is NO and the absolute value of the temperature difference ⁇ 2 is greater than or equal to the predetermined value, the process proceeds to step S17 to correct the target high pressure Pt and repeat from the high pressure F / B pressure reducing valve control in step S12 again. is there.
  • Figure 7 shows an example of correction characteristics for high-pressure correction.
  • step S15 If the temperature difference ⁇ T2 calculated in step S15 is positive (if the actual discharge temperature is less than the target discharge temperature Tt), the target high pressure Pt is positively corrected; if it is negative (the actual discharge temperature is the target discharge temperature Tt) ), The target high pressure Pt is negatively corrected.
  • step S18 If the absolute value of the temperature difference ⁇ 2 is equal to or smaller than the predetermined value and the determination result in step S16 is YES, the process proceeds to step S18, and the target high pressure is not corrected. Shifts to / B pressure reducing valve control.
  • step S19 it is determined whether or not an operation stop command has been input. If the determination result is NO and no operation stop command is input, the optimum high pressure F / B pressure reducing valve control in step S18 is performed. When the operation stop command is input and the judgment result in step S19 is YES, the above boiling operation is terminated.
  • the heat pump cycle can be changed by an external factor.
  • the stability of the cycle with respect to the movement can be improved.
  • the variation in the detected value is large. It is difficult to achieve the target COP. Therefore, the target pressure Pt is corrected from the actual discharge temperature T detected by a temperature sensor with little variation. By doing so, it is possible to achieve the target COP. In addition, if either the pressure sensor or the temperature sensor is abnormal, the pressure reducing valve can be controlled even if it is abnormal, so that the reliability of the system on the user side can be improved.
  • FIG. 8 is a flowchart showing a control example of the control device 16 in the third embodiment of the present invention.
  • the present invention controls the high-pressure F / B pressure reducing valve according to the outside air temperature detected by the outside air temperature sensor 13. It becomes a system that switches between the temperature difference and F / B pressure reducing valve control.
  • step S21 it is determined whether or not the outside air temperature is equal to or higher than a predetermined value (0 ° C. in this embodiment). If the result is YES and the outside air temperature is 0 ° C or higher, go to step 22 and set the target temperature difference to achieve the optimum COP.
  • step S23 the actual temperature difference between the inlet water temperature of the water heat exchanger 2 and the outlet refrigerant temperature.
  • FIG. 9 is a graph showing an example of control characteristics of the temperature difference F / B pressure reducing valve control in the flowchart of FIG. 8.
  • the expansion valve is throttled, and when it is negative (when the actual temperature difference ⁇ exceeds the target temperature difference A Tt), the expansion valve is opened.
  • the target temperature difference ⁇ ⁇ ⁇ t may be a predetermined value (for example, 10 ° C.) or may be calculated according to a map.
  • step S21 If the determination result in step S21 is NO and the outside air temperature is lower than 0 ° C, the routine proceeds to step 24, where the target high pressure Pt is set temporarily, and thereafter step S25 is set.
  • the pressure sensor 10 detects the high pressure while controlling the variable expansion valve 3 so that it reaches the target high pressure Pt, and the actual temperature difference between the inlet water temperature and the outlet refrigerant temperature of the water heat exchanger 2 ⁇ T Is detected, and the target high pressure Pt that has been set is corrected to the optimum value for the highest COP, and high pressure FZB pressure reducing valve control is performed.
  • the target pressure Pt is set and the refrigerant pressure on the high-pressure side is controlled so as to be the target pressure Pt, and the temperature difference ⁇ 1 between the target temperature difference ⁇ Tt and the actual temperature difference ⁇ is calculated, and the temperature difference Control that corrects the target pressure Pt so that ⁇ 1 is less than or equal to a predetermined value is at least four of the outside air temperature, the inlet refrigerant temperature of the evaporator 4 and the outlet refrigerant temperature of the air heat exchanger 4 are lower than the predetermined value. If you are going to do it.
  • 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 lower than a predetermined value (for example, 0 ° C or less) )
  • a predetermined value for example, 0 ° C or less
  • cycle stability can be improved by controlling the high pressure F / B pressure reducing valve using a pressure sensor.
  • 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 a predetermined value or high (for example, exceeding 0 ° C).
  • the boiling operation is performed by controlling the high-pressure F / B pressure reducing valve according to the target COP.
  • FIG. 10 is a flowchart showing a control example of the control device 16 according to the fourth embodiment of the present invention.
  • the present invention is a high pressure FZB pressure reducing valve according to the outside air temperature detected by the outside air temperature sensor 13. This system switches between control and discharge temperature difference F / B pressure reducing valve control.
  • step S31 it is determined whether or not the outside air temperature is equal to or higher than a predetermined value (0 ° C. in this embodiment). If the result is YES and the outside air temperature is 0 ° C or higher, step 32 Go to, and set the target discharge temperature Tt to achieve the optimal COP.
  • step S33 the actual discharge temperature T of the compressor 1 is detected, and the discharge temperature difference FZB pressure reducing valve control for controlling the variable expansion valve 3 so as to reach the target discharge temperature Tt is performed.
  • Fig. 11 is a graph showing an example of the control characteristics of the discharge temperature difference F / B pressure reducing valve control in the flowchart of Fig. 10.
  • step S31 If the determination result in step S31 is NO and the outside air temperature is lower than 0 ° C, the routine proceeds to step 34, where the target high pressure Pt is set temporarily, and thereafter, the process proceeds to step S35.
  • the pressure sensor 10 detects the high pressure and controls the variable expansion valve 3 so that the target high pressure Pt is reached.In addition, the actual temperature difference ⁇ T between the inlet water temperature and the outlet refrigerant temperature of the water heat exchanger 2 is calculated. This detects and sets the target high pressure Pt, which is corrected to the optimum value for the highest COP, and performs high pressure F / B pressure reducing valve control.
  • the target pressure Pt is set, the refrigerant pressure on the high-pressure side is controlled so that the target pressure Pt is reached, the target discharge temperature Tt of the refrigerant discharged from the compressor 1 is set, and the target discharge temperature Tt and the actual discharge are set.
  • the control to correct the target pressure Pt so that the temperature difference ⁇ ⁇ 2 with respect to the temperature T is calculated and the temperature difference ⁇ ⁇ 2 is below the specified value is controlled by the outside air temperature, the inlet refrigerant temperature of the air heat exchanger 4, and the air heat. This is performed when at least one of the outlet refrigerant temperatures of the exchanger 4 is lower than a predetermined value.
  • the temperature sensor such as a thermistor has a temperature detection delay due to the heat capacity of the functional parts and heat pump cycle. It may be difficult to control the heat in real time, and it is necessary to ensure stability against fluctuations in the heat pump cycle.
  • the stability of the cycle can be emphasized by using the pressure sensor value at the time of the low outside air temperature, and it is possible to ensure a stable heating capacity that prevents the system from abnormally stopping, and at the time of the high outside air temperature.
  • High pressure F / B pressure reducing valve control using temperature sensor value enables operation that can achieve the target COP.
  • FIG. 12 is a schematic diagram showing a configuration of a heat pump type water heater in another embodiment of the present invention.
  • the pressure reducing means is the variable expansion valve 3, but the present invention is not limited to the above-described embodiment, and as shown in FIG. 12, a heat pump cycle using an ejector 30 as the pressure reducing means. Even so, it exhibits the same effect.
  • the embodiment has been described in which the high-pressure side target pressure Pt is set when the heat pump cycle is started, but the target discharge temperature Tt of the refrigerant discharged from the compressor 1 instead of the high-pressure side target pressure Pt.
  • the same effect can be obtained by performing control for correcting the target temperature difference Tt so that the temperature difference ⁇ 2 between the target discharge temperature Tt and the actual discharge temperature is equal to or less than a predetermined value.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

Au moins au moment de démarrer un cycle de pompe à chaleur, une pression cible latérale de pression élevée (Pt) est définie, une pression réfrigérante latérale de pression élevée est commandée de façon à être la pression cible (Pt), une différence de températures (ΔT1) entre une différence de températures cible (ΔTt) et une différence de températures réelle (ΔT) est calculée, et la pression cible (Pt) est corrigée de sorte que la différence de températures (ΔT1) n’est pas supérieure à une valeur prédéterminée. Par cela, des moyens de réduction de pression (3, 30) sont directement commandés par une valeur de pression élevée détectée par un capteur de pression, etc. ayant une réponse élevée, de sorte que la stabilité d’un cycle de pompe à chaleur envers la variation du cycle causée par un facteur externe peut être améliorée. En outre, du fait que les valeurs détectées par le capteur de pression varient beaucoup pour rendre difficile l’obtention d’un COP cible, la pression cible (Pt) est corrigée en utilisant la différence de températures réelle (ΔT) détectée par un capteur de température, etc. présentant une variation inférieure dans les valeurs de détection, et ceci permet d’obtenir le COP cible.
PCT/JP2005/012800 2004-07-12 2005-07-12 Dispositif d’alimentation en eau chaude de type pompe à chaleur WO2006006578A1 (fr)

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JP2006529048A JP4337880B2 (ja) 2004-07-12 2005-07-12 ヒートポンプ式給湯器
EP05765649A EP1777471A1 (fr) 2004-07-12 2005-07-12 Dispositif d'alimentation en eau chaude de type pompe à chaleur

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JP2008039234A (ja) * 2006-08-03 2008-02-21 Daikin Ind Ltd 空気調和装置
WO2009069524A1 (fr) * 2007-11-30 2009-06-04 Mitsubishi Electric Corporation Dispositif de cycle de réfrigération
JP2013019747A (ja) * 2011-07-11 2013-01-31 Seiko Epson Corp 光学デバイス及びそれを用いた検出装置
JP2013087968A (ja) * 2011-10-13 2013-05-13 Corona Corp ヒートポンプ式給湯装置
JP2013137169A (ja) * 2011-12-28 2013-07-11 Daikin Industries Ltd ヒートポンプ式給湯機
JP2013160485A (ja) * 2012-02-08 2013-08-19 Hitachi Appliances Inc ヒートポンプ式液体加熱装置
JP2013217563A (ja) * 2012-04-09 2013-10-24 Hitachi Appliances Inc ヒートポンプ式液体加熱装置およびヒートポンプ式給湯機
JP2014016041A (ja) * 2012-07-05 2014-01-30 Denso Corp 給湯装置
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
EP4350245A4 (fr) * 2021-06-04 2024-07-10 Mitsubishi Electric Corp Unité d'alimentation en eau chaude de type à stockage d'eau chaude

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JP5452581B2 (ja) * 2011-12-29 2014-03-26 三菱電機株式会社 ヒートポンプシステム及びヒートポンプ装置の制御方法
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
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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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Cited By (14)

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Publication number Priority date Publication date Assignee Title
JP2008039234A (ja) * 2006-08-03 2008-02-21 Daikin Ind Ltd 空気調和装置
US8104299B2 (en) 2006-08-03 2012-01-31 Daikin Industries, Ltd. Air conditioner
WO2009069524A1 (fr) * 2007-11-30 2009-06-04 Mitsubishi Electric Corporation Dispositif de cycle de réfrigération
JP2009133547A (ja) * 2007-11-30 2009-06-18 Mitsubishi Electric Corp 冷凍サイクル装置
CN101842645B (zh) * 2007-11-30 2012-11-28 三菱电机株式会社 冷冻循环装置
JP2013019747A (ja) * 2011-07-11 2013-01-31 Seiko Epson Corp 光学デバイス及びそれを用いた検出装置
JP2013087968A (ja) * 2011-10-13 2013-05-13 Corona Corp ヒートポンプ式給湯装置
JP2013137169A (ja) * 2011-12-28 2013-07-11 Daikin Industries Ltd ヒートポンプ式給湯機
JP2013160485A (ja) * 2012-02-08 2013-08-19 Hitachi Appliances Inc ヒートポンプ式液体加熱装置
JP2013217563A (ja) * 2012-04-09 2013-10-24 Hitachi Appliances Inc ヒートポンプ式液体加熱装置およびヒートポンプ式給湯機
JP2014016041A (ja) * 2012-07-05 2014-01-30 Denso Corp 給湯装置
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
EP4350245A4 (fr) * 2021-06-04 2024-07-10 Mitsubishi Electric Corp Unité d'alimentation en eau chaude de type à stockage d'eau chaude

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