EP3431896A1 - Distributeur d'eau chaude à pompe à chaleur - Google Patents

Distributeur d'eau chaude à pompe à chaleur Download PDF

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Publication number
EP3431896A1
EP3431896A1 EP16894400.7A EP16894400A EP3431896A1 EP 3431896 A1 EP3431896 A1 EP 3431896A1 EP 16894400 A EP16894400 A EP 16894400A EP 3431896 A1 EP3431896 A1 EP 3431896A1
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EP
European Patent Office
Prior art keywords
temperature
water
refrigerant
sensor
heat exchanger
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.)
Granted
Application number
EP16894400.7A
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German (de)
English (en)
Other versions
EP3431896A4 (fr
EP3431896B1 (fr
Inventor
Kensaku HATANAKA
Toru Koide
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3431896A4 publication Critical patent/EP3431896A4/fr
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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
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1051—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
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/174—Supplying heated water with desired temperature or desired range of 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
    • F24H15/20—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
    • F24H15/232—Temperature of the refrigerant in heat pump cycles at the condenser
    • 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
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/04—Sensors
    • F24D2220/042—Temperature sensors
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • 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
    • F25B2600/13—Pump speed control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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

Definitions

  • the present invention relates to a heat pump water heater apparatus having a water circuit and a refrigerant circuit using carbon dioxide as refrigerant, in which heat is exchanged between water flowing through the water circuit and the carbon dioxide flowing through the refrigerant circuit.
  • a heat pump water heater apparatus having a water circuit and a refrigerant circuit using hydrocarbon (HC) refrigerant
  • an opening degree of an expansion valve is controlled so that a temperature difference between a discharge temperature of refrigerant discharged from a compressor and an outflow water temperature of water flowing out of a water heating heat exchanger becomes a target value determined so that the coefficient of performance (COP) is maximized (for example, see Patent Literature 1).
  • COP coefficient of performance
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2012-233626 (Claim 1, Page 9)
  • Patent Literature 1 As one type of refrigerant circulating through the refrigerant circuit, carbon dioxide is known. Carbon dioxide has advantages such as incombustibility and low global warming potential, but has such a characteristic that a pressure in the refrigerant circuit is higher as compared to that of hydrocarbon refrigerant.
  • Patent Literature 1 there is a description that, in the heat pump water heater apparatus using hydrocarbon refrigerant, the opening degree of the expansion valve is controlled so that the temperature difference between the discharge refrigerant temperature of the refrigerant discharged from the compressor and the outflow water temperature becomes the target value determined so that the coefficient of performance (COP) is maximized.
  • the control adopted in Patent Literature 1 could not be applied to the heat pump water heater apparatus using carbon dioxide. The reason is as follows.
  • the carbon dioxide has a high pressure in the refrigerant circuit, and hence when the target temperature difference between the discharge refrigerant temperature and the outflow water temperature is determined so that the COP is maximized, the high-pressure-side pressure may exceed a design pressure. In this case, a heat pump operation cannot be continued, and the water heating is stopped. Further, there is also a characteristic in which the high pressure of the carbon dioxide tends to rise when the temperature of water to be heated by carbon dioxide is high, and hence management of the high pressure is important. A technology has been desired that enables the heat pump water heater apparatus using carbon dioxide to perform stable water heating operation while the rise of the high pressure is suppressed.
  • the present invention has been made in view of the above-mentioned problem, and provides a heat pump water heater apparatus using carbon dioxide as refrigerant and capable of performing stable water heating operation while rise of a high pressure is suppressed.
  • a heat pump water heater apparatus having a water circuit and a refrigerant circuit thermally connected through a first heat exchanger, the refrigerant circuit circulating carbon dioxide, the first heat exchanger being configured to exchange heat between the water and the carbon dioxide, the refrigerant circuit including a compressor, a refrigerant passage of the first heat exchanger, an expansion valve, and a second heat exchanger, the water circuit including a water passage of the first heat exchanger and a tank, the heat pump water heater apparatus including: a first sensor configured to detect a temperature of the carbon dioxide discharged from the compressor, a second sensor configured to detect a temperature of the water flowing into the water passage; and a third sensor configured to detect a temperature of the water flowing out of the water passage; the expansion valve being opened to have an opening degree to reduce a difference between a first value and a target value, the first value being a difference between a temperature detected by the third sensor and a temperature detected by the first sensor, the target value being determined to be
  • the heat pump water heater apparatus having the refrigerant circuit using carbon dioxide as refrigerant can perform stable water heating operation while the rise of the high pressure of the refrigerant discharged from the compressor is suppressed.
  • Heat pump water heater apparatus according to embodiments of the present invention are described with reference to the drawings.
  • relative dimensional relationships or shapes of respective components may differ from actual ones.
  • FIG. 1 is a circuit configuration diagram for illustrating a heat pump water heater apparatus according to Embodiment 1 of the present invention.
  • a heat pump water heater apparatus 100 has a refrigerant circuit 10 circulating carbon dioxide serving as refrigerant, and a water circuit 20.
  • the refrigerant circuit 10 and the water circuit 20 are thermally connected through a first heat exchanger 12 serving as a water-refrigerant heat exchanger, and the first heat exchanger 12 exchanges heat between the refrigerant circulating through the refrigerant circuit 10 and water circulating through the water circuit 20.
  • the refrigerant circuit 10 includes a compressor 11 configured to compress and discharge the refrigerant, a refrigerant passage 12a of the first heat exchanger 12 through which the refrigerant discharged from the compressor 11 passes, an expansion valve 13 configured to decompress the refrigerant, and a second heat exchanger 14, which are annularly connected in the stated order by a refrigerant pipe 18.
  • the compressor 11 is driven by a driver including, for example, an inverter-controlled DC brushless motor, and has a function of varying the pressure and the temperature of the refrigerant discharged from the compressor 11.
  • the expansion valve 13 has a variable opening degree, and has a function of varying a decompression state of the refrigerant passing therethrough.
  • an accumulator 15 which is a container for accumulating surplus refrigerant, is connected on the downstream side of the second heat exchanger 14 and on the upstream side of the compressor 11.
  • the second heat exchanger 14 is an air heat exchanger configured to exchange heat between the refrigerant circuiting through the refrigerant circuit 10 and outdoor air.
  • a fan 16 configured to send the outdoor air to the second heat exchanger 14 is arranged in the vicinity of the second heat exchanger 14.
  • a first sensor 17 that is a temperature sensor configured to detect a temperature of the refrigerant discharged from the compressor 11 is provided.
  • the first sensor 17 is a temperature sensor configured to detect the temperature of the refrigerant directly or indirectly via a pipe.
  • the water circuit 20 includes a tank 21 for storing water and a water passage 12b of the first heat exchanger 12, which are connected by a water circulating pipe 25.
  • a pump 22 configured to send water is arranged in the water circulating pipe 25.
  • the pump 22 is operated to circulate water in the water circuit 20.
  • One end of the water circulating pipe 25 is connected to a lower portion of the tank 21, and an other end of the water circulating pipe 25 is connected to an upper portion of the tank 21. Water having a relatively low temperature at the lower portion of the tank 21 is heated by the first heat exchanger 12 to flow into the tank 21 from the upper portion of the tank 21.
  • a water supply pipe 26 that is different from the water circulating pipe 25 is connected. Water from a water supply source is stored in the tank 21 via the water supply pipe 26. To the upper portion of the tank 21, an outflow water pipe 27 that is different from the water circulating pipe 25 is connected. Water having a relatively high temperature at the upper portion of the tank 21 is supplied to, for example, a bathtub.
  • the pipe configurations related to water supply to the tank 21 and water outflow from the tank 21 are merely an example, and the present invention is not limited to those pipe configurations.
  • a second sensor 23 that is a temperature sensor configured to detect a temperature of water flowing into the first heat exchanger 12 is provided.
  • a third sensor 24 that is a temperature sensor configured to detect a temperature of water flowing out of the first heat exchanger 12 is provided.
  • a water inlet temperature T wi detected by the second sensor 23 is a temperature of water before being heated by the first heat exchanger 12
  • a water outlet temperature T wo detected by the third sensor 24 is a temperature of water after being heated by the first heat exchanger 12.
  • the second sensor and the third sensor are temperature sensors configured to detect the temperature of the water directly or indirectly via a pipe.
  • the heat pump water heater apparatus 100 includes an outdoor air temperature detection device 28 that is a temperature sensor.
  • the outdoor air temperature detection device 28 is arranged at a place at which an outdoor air temperature in the vicinity of the heat pump water heater apparatus 100 can be measured.
  • Fig. 2 is a functional block diagram for illustrating the heat pump water heater apparatus according to Embodiment 1.
  • the heat pump water heater apparatus 100 includes a controller 30 configured to control the entirety of the apparatus, and the controller 30 includes a memory 31.
  • the controller 30 receives input such as output of the first sensor 17, the second sensor 23, the third sensor 24, and the outdoor air temperature detection device 28 and information from operation means operated by a user.
  • the controller 30 outputs commands to the compressor 11, the expansion valve 13, the fan 16, and the pump 22 based on those pieces of input information to control the operation of those actuators.
  • the controller 30 controls a frequency of the driver for the compressor 11 to control the operation state of the compressor 11 so that the pressure and the temperature of the discharged refrigerant are adjusted.
  • the controller 30 controls the opening degree of the expansion valve 13 so that the refrigerant attains a target decompression state in the expansion valve 13.
  • the controller 30 controls the operation states of the fan 16 and the pump 22.
  • the controller 30 is constructed of dedicated hardware or a central processing unit (CPU, also referred to as central processing device, processing device, calculation device, microprocessor, microcomputer, and processor) configured to execute a program stored in the memory 31.
  • CPU central processing unit
  • the controller 30 When the controller 30 is dedicated hardware, the controller 30 corresponds to, for example, a single circuit, a composite circuit, an application specific integrated circuit (ASIC), a field-programmable gate array (FPGA), or a combination of those circuits.
  • ASIC application specific integrated circuit
  • FPGA field-programmable gate array
  • Each functional unit to be implemented by the controller 30 may be implemented by individual hardware, or the functional units may be implemented by single hardware.
  • each function executed by the controller 30 is implemented by software, firmware, or a combination of software and firmware.
  • the software or the firmware is described as a program, and stored in the memory 31.
  • the CPU loads and executes the program stored in the memory 31 to implement the functions of the controller 30.
  • the memory 31 is a non-volatile or volatile semiconductor memory, for example, a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.
  • a part of the functions of the controller 30 may be implemented by dedicated hardware, and a part may be implemented by software or firmware. Further, in Fig. 2 , the respective actuators are controlled collectively by the controller 30, but the controller 30 is not necessarily required to be physically configured as illustrated in Fig. 2 . That is, specific forms of dispersion and integration of the controller 30 are not limited to those illustrated in Fig. 2 , and the whole or a part thereof may be functionally or physically dispersed or integrated in any unit in accordance with various loads or use conditions, for example.
  • the overall description of water heating operation of the heat pump water heater apparatus 100 is provided below.
  • the compressor 11 whose operation frequency is controlled, is operated, the compressed refrigerant is discharged from the compressor 11.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the refrigerant passage 12a of the first heat exchanger 12.
  • the pump 22 is driven, and the action of the pump 22 causes water in the tank 21 to pass through the water circulating pipe 25 to flow into the water passage 12b of the first heat exchanger 12.
  • the high-temperature and high-pressure refrigerant passing through the refrigerant passage 12a and the water passing through the water passage 12b exchange heat in the first heat exchanger 12, and the refrigerant decreased in temperature and the high-temperature water increased in temperature respectively flow out of the first heat exchanger 12.
  • the high-temperature water increased in temperature in the first heat exchanger 12 passes through the water circulating pipe 25 to flow into the tank 21.
  • the refrigerant flowing into the expansion valve 13 is decompressed to a state corresponding to the opening degree of the expansion valve 13, and transitions to the low-pressure refrigerant to flow into the second heat exchanger 14.
  • the refrigerant flowing into the second heat exchanger 14 exchanges heat with the outdoor air in the process of passing through the second heat exchanger 14 and is increased in temperature.
  • the operation state of the fan 16 is controlled so as to obtain a desired heat exchange amount between the outdoor air and the refrigerant.
  • the refrigerant increased in temperature through heat exchange with the outdoor air in the second heat exchanger 14 is sucked into the compressor 11 via the accumulator 15.
  • the controller 30 monitors the high-pressure-side refrigerant pressure output from the first sensor 17, and when the high-pressure-side refrigerant pressure exceeds an upper limit value determined at the time of design, the controller 30 temporarily stops the water heating operation.
  • Fig. 3 is a flow chart for illustrating the control of the refrigerant circuit of the heat pump water heater apparatus according to Embodiment 1.
  • the controller 30 determines a driving frequency of the compressor 11, and operates the compressor 11 at the determined driving frequency. Specifically, the controller 30 determines the driving frequency of the compressor 11 based on an outdoor air temperature T a output from the outdoor air temperature detection device 28 and the water inlet temperature T wi output from the second sensor 23.
  • the driving frequency of the compressor 11 is set higher in a case where the outdoor air temperature T a is low, than in a case where the outdoor air temperature T a is high. Further, the driving frequency of the compressor 11 is set higher in a case where the water inlet temperature T wi is low, than in a case where the water inlet temperature T wi is high.
  • a correspondence table between a combination of the outdoor air temperature T a and the water inlet temperature T wi and the driving frequency of the compressor 11 is obtained through experiments or other methods in advance, and the correspondence table is stored in the memory 31.
  • the controller 30 can determine the driving frequency based on the correspondence table stored in the memory 31. Instead of determining the driving frequency based on the correspondence table as described above, the controller 30 may determine the driving frequency by applying the detected outdoor air temperature T a and water inlet temperature T wi to a predetermined calculation formula.
  • the controller 30 sets a target temperature difference ⁇ T _t that is a target value of a temperature difference between a discharge refrigerant temperature T ro and a target water outlet temperature T wo_t .
  • the target water outlet temperature T wo_t is set based on a predetermined temperature of the water to be stored in the tank 21.
  • the discharge refrigerant temperature T ro is set as a temperature that is higher than the target water outlet temperature T wo_t by an amount of a margin so that the temperature of the water to be heated by the refrigerant in the first heat exchanger 12 reaches the target water outlet temperature T wo_t .
  • the value of the amount of the margin corresponds to the target temperature difference ⁇ T _t .
  • the target temperature difference ⁇ T _t is set to a value corresponding to the target water outlet temperature T wo_t .
  • a correspondence table between the target water outlet temperature T wo_t and the target temperature difference ⁇ T _t can be stored in the memory 31 in advance.
  • the controller 30 corrects the target temperature difference ⁇ T _t set in Step S2. Specifically, the controller 30 corrects the target temperature difference ⁇ T _t so that the target temperature difference ⁇ T _t is smaller in a case where the water inlet temperature T wi output from the second sensor 23 is a first temperature V 1 , than in a case of a second temperature V 2 (provided that V 1 >V 2 ). That is, even at the same target water outlet temperature T wo_t , the target temperature difference ⁇ T _t is changed depending on the water inlet temperature T wi , and the target temperature difference ⁇ T _t is determined to be smaller in a case where the water inlet temperature T wi is large, than in a case where the water inlet temperature T wi is small.
  • Fig. 4 is an example of a graph of a relationship between the water inlet temperature and the target temperature difference in the heat pump water heater apparatus according to Embodiment 1.
  • Fig. 4 shows an example in which the correction value of the target temperature difference ⁇ T _t is changed stepwise so that the target temperature difference ⁇ T _t is decreased as the water inlet temperature T wi is increased.
  • the target temperature difference ⁇ T _t may be corrected by determining one threshold value for the water inlet temperature T wi in advance, and subtracting a predetermined correction value from the target temperature difference ⁇ T _t when the water inlet temperature T wi exceeds the threshold value.
  • Fig. 5 is another example of the graph of the relationship between the water inlet temperature and the target temperature difference in the heat pump water heater apparatus according to Embodiment 1.
  • the target temperature difference ⁇ T _t may be corrected by adjusting the correction value in accordance with the outdoor air temperature T a in addition to the adjustment to the water inlet temperature T wi .
  • T a ⁇ degrees Celsius
  • the controller 30 controls the opening degree of the expansion valve 13 so that a temperature difference ⁇ T between the discharge refrigerant temperature T ro detected by the first sensor 17 and the water outlet temperature T wo detected by the third sensor 24 approaches the target temperature difference ⁇ T _t corrected in Step S3.
  • Step S4 While the operation of Step S4 is executed, the pump 22 is operated to cause the water from the lower portion of the tank 21 to pass through the water passage 12b of the first heat exchanger 12. In this process, the water is heated by the refrigerant, and the heated water is returned into the tank 21 from the upper portion of the tank 21. In this manner, the boiled high-temperature water is stored in the tank 21.
  • the rotation speed of the pump 22 is controlled so that the output value of the third sensor 24 becomes the target water outlet temperature T wo_t .
  • the opening degree of the expansion valve 13 is controlled so as to obtain the target temperature difference ⁇ T _t in Step S4, that is, the heating capacity is maintained constant in the heat pump cycle, and hence the water outlet temperature T wo can be secured by adjusting the rotation speed of the pump 22.
  • the controller 30 continuously performs the processing of Step S4 until the boiling is finished.
  • the controller 30 determines that the boiling is finished, and ends the operation.
  • the opening degree of the expansion valve 13 is controlled so that the difference between the target temperature difference ⁇ T _t and the temperature difference ⁇ T between the discharge refrigerant temperature T ro and the water outlet temperature T wo is decreased.
  • the value of the target temperature difference ⁇ T _t is set to be smaller in a case where the water inlet temperature T wi is the first temperature, than in a case of the second temperature that is smaller than the first temperature. Therefore, the opening degree of the expansion valve 13 is controlled so that the degree of superheat of carbon dioxide serving as the refrigerant is lower in a case where the water inlet temperature T wi is high, than in a case where the water inlet temperature T wi is low.
  • the controller 30 temporarily stops the water heating operation when the high-pressure-side refrigerant pressure exceeds the upper limit value determined at the time of design, but the high pressure of the refrigerant is prevented from excessively rising according to Embodiment 1. Therefore, the water heating operation can be continued stably, and the heat pump water heater apparatus 100 having high reliability can be obtained.
  • the first value of the invention of the subject application corresponds to the temperature difference ⁇ T in Embodiment 1.
  • Embodiment 2 of the present invention a modification example of above-mentioned Embodiment 1 is described.
  • description is given of correcting the target temperature difference ⁇ T _t based on the water inlet temperature T wi , but in Embodiment 2, description is given of controlling the minimum value of the target temperature difference ⁇ T _t after the correction.
  • Embodiment 2 is achieved by adding a configuration to Embodiment 1, and the difference from Embodiment 1 is mainly described below.
  • Fig. 6 is a configuration diagram for illustrating an accumulator according to Embodiment 2.
  • pipes of the refrigerant circuit 10 are inserted to an upper portion and a lower portion of the accumulator 15.
  • the refrigerant flows into the accumulator 15 from the pipe at the upper portion, and gas refrigerant flows out of the pipe at the lower portion.
  • the refrigerant flowing out of the accumulator 15 is sucked into the compressor 11.
  • the accumulator 15 includes a liquid level gauge 19 configured to detect the liquid level of the liquid refrigerant in the accumulator 15.
  • the specific configuration of the liquid level gauge 19 is not particularly limited as long as the liquid level gauge has a function of detecting the liquid level of the liquid refrigerant. Any liquid level gauge of, for example, a magnet float type, a capacitive type, or an ultrasonic type can be used.
  • Fig. 7 is a functional block diagram for illustrating a heat pump water heater apparatus according to Embodiment 2. As illustrated in Fig. 7 , the liquid level gauge 19 is connected to the controller 30 so that communication is enabled therebetween, and the output of the liquid level gauge 19 is input to the controller 30.
  • the operation control related to the water heating capacity in the refrigerant circuit 10 of the heat pump water heater apparatus 100 is performed similarly to that illustrated in Fig. 3 in Embodiment 1. That is, the target temperature difference ⁇ T _t between the discharge refrigerant temperature T ro and the target water outlet temperature T wo_t is corrected based on the water inlet temperature T wi . Then, the opening degree of the expansion valve 13 is controlled so that the temperature difference ⁇ T between the detected discharge refrigerant temperature T ro and the water outlet temperature T wo becomes the target temperature difference ⁇ T _t after the correction.
  • the value of the target temperature difference ⁇ T _t is corrected so that the value is smaller as the water inlet temperature T wi is higher, but when the liquid level gauge 19 detects that the liquid level in the accumulator 15 exceeds a threshold value, the downward correction of the target temperature difference ⁇ T _t is not performed. That is, when the liquid level gauge 19 detects the threshold value, the controller 30 maintains the value of the target temperature difference ⁇ T _t at the current state or increases the value to be larger than the current value irrespective of the detected water inlet temperature T wi .
  • the controller 30 performs correction of decreasing the target temperature difference ⁇ T _t as the water inlet temperature T wi is increased until the amount of the liquid refrigerant in the accumulator 15 reaches the threshold value.
  • the rise of the high pressure of the refrigerant discharged from the compressor 11 can be suppressed.
  • the controller 30 does not perform correction of decreasing the target temperature difference ⁇ T _t , and hence the shortage of the amount of refrigerant circulating through the refrigerant circuit 10 can be prevented.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP16894400.7A 2016-03-17 2016-03-17 Distributeur d'eau chaude à pompe à chaleur Active EP3431896B1 (fr)

Applications Claiming Priority (1)

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PCT/JP2016/058439 WO2017158782A1 (fr) 2016-03-17 2016-03-17 Distributeur d'eau chaude à pompe à chaleur

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CN108800562B (zh) * 2018-06-20 2020-06-02 青岛海信日立空调系统有限公司 热水热泵系统的制热控制方法、装置及系统
CN109826781B (zh) * 2018-12-28 2020-01-21 合肥通用机械研究院有限公司 具备跨/亚临界测试功能的二氧化碳压缩机性能试验系统
CN113325028B (zh) * 2021-06-07 2022-05-24 中国核动力研究设计院 自然循环系统不稳定流动的沸腾临界实验装置及控制方法
CN113432298B (zh) * 2021-06-28 2022-03-22 珠海格力电器股份有限公司 压缩系统的控制方法、装置及空气能热泵热水器
CN113483385B (zh) * 2021-07-02 2022-10-04 青岛海信日立空调系统有限公司 一种空气源热泵机组

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NO890076D0 (no) * 1989-01-09 1989-01-09 Sinvent As Luftkondisjonering.
JP3227651B2 (ja) * 1998-11-18 2001-11-12 株式会社デンソー 給湯器
US7076964B2 (en) * 2001-10-03 2006-07-18 Denso Corporation Super-critical refrigerant cycle system and water heater using the same
JP3801169B2 (ja) * 2003-11-19 2006-07-26 松下電器産業株式会社 ヒートポンプ給湯装置
JP3900186B2 (ja) * 2005-02-10 2007-04-04 松下電器産業株式会社 ヒートポンプ給湯機
JP5168344B2 (ja) * 2010-11-24 2013-03-21 三菱電機株式会社 ヒートポンプ式給湯機
JP5776314B2 (ja) 2011-04-28 2015-09-09 株式会社ノーリツ ヒートポンプ給湯機

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JPWO2017158782A1 (ja) 2018-09-27
WO2017158782A1 (fr) 2017-09-21
EP3431896B1 (fr) 2019-11-06
JP6537703B2 (ja) 2019-07-03

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