WO2017158782A1 - 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
WO2017158782A1
WO2017158782A1 PCT/JP2016/058439 JP2016058439W WO2017158782A1 WO 2017158782 A1 WO2017158782 A1 WO 2017158782A1 JP 2016058439 W JP2016058439 W JP 2016058439W WO 2017158782 A1 WO2017158782 A1 WO 2017158782A1
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WIPO (PCT)
Prior art keywords
temperature
heat exchanger
sensor
value
refrigerant
Prior art date
Application number
PCT/JP2016/058439
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English (en)
Japanese (ja)
Inventor
謙作 畑中
徹 小出
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2018505157A priority Critical patent/JP6537703B2/ja
Priority to PCT/JP2016/058439 priority patent/WO2017158782A1/fr
Priority to EP16894400.7A priority patent/EP3431896B1/fr
Publication of WO2017158782A1 publication Critical patent/WO2017158782A1/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 having a refrigerant circuit and a hot water supply circuit using carbon dioxide as a refrigerant and exchanging heat between water flowing through the hot water supply circuit and carbon dioxide flowing through the refrigerant circuit.
  • Carbon dioxide is a type of refrigerant circulating in the refrigerant circuit. Carbon dioxide has a merit that it is nonflammable and has a low global warming potential, but has a characteristic that the pressure in the refrigerant circuit is higher than that of hydrocarbon refrigerant.
  • the temperature difference between the refrigerant discharge refrigerant temperature and the tapping temperature is such that the COP (Coefficient ⁇ of ⁇ Performance) is maximized.
  • the control adopted in Patent Document 1 cannot be applied to a heat pump water heater using carbon dioxide.
  • the present invention has been made against the background of the above-described problems, and provides a heat pump water heater using carbon dioxide as a refrigerant that can suppress a rise in high pressure and perform a stable hot water supply operation. .
  • the heat pump water heater of the present invention has a refrigerant circuit and a hot water supply circuit in which carbon dioxide circulates, and a heat pump in which water flowing through the hot water supply circuit and the carbon dioxide flowing through the refrigerant circuit exchange heat with a first heat exchanger.
  • the refrigerant circuit includes a compressor, a refrigerant flow path of the first heat exchanger, an expansion valve, and a second heat exchanger, and the hot water supply circuit includes the first heat exchanger.
  • the heat pump water heater has a water flow path and a tank, and the heat pump water heater detects the temperature of the carbon dioxide discharged from the compressor, and the temperature of water flowing into the water flow path of the first heat exchanger And a third sensor for detecting the temperature of water flowing out of the water flow path of the first heat exchanger, and the expansion valve has a difference between the first value and the target value.
  • the opening degree is set to decrease, and the first value is the third value.
  • the target value is a second temperature that is lower than the first temperature when the detection value of the second sensor is the first temperature. This is a smaller value than the case of.
  • a stable hot water supply operation can be performed while suppressing an increase in the high pressure of the refrigerant discharged from the compressor.
  • FIG. 1 is a circuit configuration diagram of a heat pump water heater according to Embodiment 1.
  • FIG. 3 is a functional block diagram of the heat pump water heater according to Embodiment 1.
  • FIG. 3 is a flowchart relating to control of a refrigerant circuit of the heat pump water heater according to the first embodiment. It is an example of the relationship figure of the water inlet temperature of the heat pump water heater which concerns on Embodiment 1, and target temperature difference. It is another example of the relationship figure of the water inlet temperature of the heat pump water heater which concerns on Embodiment 1, and target temperature difference.
  • 6 is a configuration diagram of an accumulator according to Embodiment 2.
  • FIG. It is a functional block diagram of the heat pump water heater according to the second embodiment.
  • FIG. 1 is a circuit configuration diagram of the heat pump water heater according to the first embodiment.
  • the heat pump water heater 100 includes a refrigerant circuit 10 in which carbon dioxide as a refrigerant circulates, and a hot water supply circuit 20.
  • the refrigerant circuit 10 and the hot water supply circuit 20 are thermally connected in the first heat exchanger 12 which is a water refrigerant heat exchanger, and the refrigerant circulating in the refrigerant circuit 10 and the water circulating in the hot water supply circuit 20 are first connected.
  • 1 Heat exchange is performed by the heat exchanger 12.
  • the refrigerant circuit 10 includes a compressor 11 that compresses and discharges the refrigerant, a refrigerant flow path 12a of the first heat exchanger 12 through which the refrigerant discharged from the compressor 11 passes, an expansion valve 13 that decompresses the refrigerant,
  • the second heat exchanger 14 is configured to be annularly connected by the refrigerant pipe 18 in this order.
  • the compressor 11 is driven by a driving device including, for example, an inverter-controlled DC brushless motor, and has a function of making the pressure and temperature of refrigerant discharged from the compressor 11 variable.
  • the expansion valve 13 has a structure in which the opening degree of the valve can be adjusted, and has a function of changing the decompression state of the refrigerant passing therethrough.
  • an accumulator 15 which is a container for storing excess refrigerant, is connected to the downstream side of the second heat exchanger 14 and the upstream side of the compressor 11.
  • the second heat exchanger 14 is an air heat exchanger that performs heat exchange between the refrigerant circulating in the refrigerant circuit 10 and the outside air.
  • a blower 16 that blows outside air to the second heat exchanger 14 is installed around the second heat exchanger 14.
  • the discharge part of the compressor 11 is provided with a first sensor 17 that is a temperature sensor that detects the temperature of the refrigerant discharged from the compressor 11.
  • the 1st sensor 17 is a temperature sensor which detects the temperature of a refrigerant directly or indirectly via piping.
  • the hot water supply circuit 20 is configured by connecting a tank 21 for storing water and a water flow path 12 b of the first heat exchanger 12 by a water circulation pipe 25.
  • the water circulation pipe 25 is provided with a pump 22 for sending water, and the water is circulated in the hot water supply circuit 20 by operating the pump 22.
  • One end of the water circulation pipe 25 is connected to the lower part of the tank 21, and the other end of the water circulation pipe 25 is connected to the upper part of the tank 21, so that the relatively low temperature water in the lower part of the tank 21 is subjected to the first heat exchange.
  • the tank 12 is heated and flows into the tank 21 from the upper part of the tank 21.
  • a water supply pipe 26 different from the water circulation pipe 25 is connected to the lower part of the tank 21, and water from the water supply source is stored in the tank 21 through the water supply pipe 26.
  • a hot water supply pipe 27 different from the water circulation pipe 25 is connected to the upper part of the tank 21, and relatively high-temperature water in the upper part of the tank 21 is supplied to, for example, a bathtub.
  • the piping structure which concerns on the water supply to the tank 21 and the tapping from the tank 21 is an example, and this invention is not limited by these piping structures.
  • a third sensor 24 that is a temperature sensor that detects the temperature of water flowing out of the first heat exchanger 12 is provided at the outlet of the water flow path 12 b of the first heat exchanger 12.
  • Water inlet temperature T wi detected by the second sensor 23 is a temperature of the water before being heated in the first heat exchanger 12, the water outlet temperature T wo detected by the third sensor 24, the first The temperature of the water after being heated by the heat exchanger 12.
  • a 2nd sensor and a 3rd sensor are temperature sensors which detect the temperature of water directly or indirectly through piping.
  • the heat pump water heater 100 includes an outside air temperature detection device 28 that is a temperature sensor.
  • the outside air temperature detection device 28 is installed in a place where the outside air temperature around the heat pump water heater 100 can be measured.
  • FIG. 2 is a functional block diagram of the heat pump water heater according to the first embodiment.
  • the heat pump water heater 100 includes a control device 30 that performs overall control, and the control device 30 includes a memory 31.
  • the control device 30 receives the output of the first sensor 17, the second sensor 23, the third sensor 24, and the outside air temperature detection device 28, information from the operating means operated by the user, and the like.
  • the control device 30 controls the operation of these actuators by issuing commands to the compressor 11, the expansion valve 13, the blower 16, and the pump 22 based on these input information.
  • the control device 30 controls the operating state of the compressor 11 so as to adjust the pressure and temperature of the refrigerant to be discharged by controlling the frequency of the drive device of the compressor 11.
  • the control device 30 controls the opening degree of the expansion valve 13 so that the refrigerant reaches the target decompression state in the expansion valve 13.
  • the control device 30 controls the operating states of the blower 16 and the pump 22.
  • the control device 30 is configured by dedicated hardware or a CPU (also referred to as a central processing unit, a central processing device, a processing device, an arithmetic device, a microprocessor, a microcomputer, or a processor) that executes a program stored in the memory 31.
  • a CPU also referred to as a central processing unit, a central processing device, a processing device, an arithmetic device, a microprocessor, a microcomputer, or a processor
  • control device 30 When the control device 30 is dedicated hardware, the control device 30 may be, for example, a single circuit, a composite circuit, an ASIC (application specific integrated circuit), an FPGA (field-programmable gate array), or a combination thereof. Applicable. Each functional unit realized by the control device 30 may be realized by individual hardware, or each functional unit may be realized by one piece of hardware.
  • ASIC application specific integrated circuit
  • FPGA field-programmable gate array
  • each function executed by the control device 30 is realized by software, firmware, or a combination of software and firmware.
  • Software and firmware are described as programs and stored in the memory 31.
  • the CPU implements each function of the control device 30 by reading and executing the program stored in the memory 31.
  • the memory 31 is, for example, a nonvolatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.
  • control device 30 may be realized by dedicated hardware, and a part may be realized by software or firmware.
  • control of the respective actuators is illustrated as being controlled by the control device 30, but the control device 30 does not necessarily have to be physically configured as illustrated. That is, the specific form of distribution and integration of the control device 30 is not limited to the illustrated one, and all or a part thereof is functionally or physically distributed in arbitrary units according to various loads or usage conditions. Alternatively, they can be integrated.
  • the outline of the hot water supply operation of the heat pump water heater 100 will be described.
  • the frequency-controlled compressor 11 When the frequency-controlled compressor 11 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 flow path 12a of the first heat exchanger 12.
  • the pump 22 is driven, and the water in the tank 21 flows into the water flow path 12 b of the first heat exchanger 12 through the water circulation pipe 25 by the action of the pump 22.
  • the high-temperature and high-pressure refrigerant passing through the refrigerant flow path 12a and the water passing through the water flow path 12b are heat-exchanged in the first heat exchanger 12, and the refrigerant whose temperature has decreased and the high-temperature water whose temperature has increased respectively.
  • the high-temperature water whose temperature has risen in the first heat exchanger 12 flows into the tank 21 through the water circulation pipe 25.
  • the refrigerant whose temperature has decreased due to heat exchange with water in the first heat exchanger 12 flows into the expansion valve 13.
  • the refrigerant flowing into the expansion valve 13 is depressurized to a state corresponding to the opening degree of the expansion valve 13, and becomes a low-pressure refrigerant and flows into the second heat exchanger 14.
  • the refrigerant flowing into the second heat exchanger 14 exchanges heat with the outside air in the process of passing through the second heat exchanger 14, and the temperature rises.
  • the operation state of the blower 16 is controlled in order to obtain a desired heat exchange amount between the outside air and the refrigerant.
  • the refrigerant whose temperature has risen due to heat exchange with the outside air in the second heat exchanger 14 is sucked into the compressor 11 via the accumulator 15.
  • the control device 30 monitors the high-pressure side refrigerant pressure output from the first sensor 17, and temporarily stops the hot water supply operation when the high-pressure side refrigerant pressure exceeds the upper limit value determined at the time of design. It
  • FIG. 3 is a flowchart relating to the control of the refrigerant circuit of the heat pump water heater according to the first embodiment.
  • the control device 30 determines the drive frequency of the compressor 11 and operates the compressor 11 at the determined drive frequency. Specifically, the control device 30 determines the drive frequency of the compressor 11 based on the outside air temperature T a output from the outside air temperature detector 28 and the water inlet temperature T wi output from the second sensor 23. To do. If the outside air temperature T a is lower than is higher, the driving frequency of the compressor 11 is set high. Further, when the water inlet temperature Twi is low, the drive frequency of the compressor 11 is determined to be higher than when the water inlet temperature Twi is high. For example, previously obtained by test etc.
  • correspondence table between a combination and the driving frequency of the compressor 11 with the outside air temperature T a and the water inlet temperature T wi stores the correspondence table in the memory 31, the controller 30 memory
  • the drive frequency can be determined based on the correspondence table stored in 31. Instead of determining the driving frequency based on such a correspondence table, the control unit 30 applies a predetermined operation expression the detected outside air temperature T a and the water inlet temperature T wi, the drive frequency May be determined.
  • T _t is a target value of the temperature difference between the discharged refrigerant temperature T ro and the target water outlet temperature T wo_t.
  • the target water outlet temperature Two_t is set based on a predetermined temperature of water stored in the tank 21. Discharged refrigerant temperature T ro, as the temperature of the water heated by the refrigerant in the first heat exchanger 12 becomes equal to the target water outlet temperature T Wo_t, as higher temperatures only margin allowance with respect to the target water outlet temperature T Wo_t Is set.
  • the value for the margin is the target temperature difference ⁇ T_t .
  • Target temperature difference [Delta] T _t the value corresponding to the target water outlet temperature T Wo_t is set. For example, it can be stored in advance in the memory 31 a correspondence table between the target water outlet temperature T Wo_t and the target temperature difference [Delta] T _t.
  • the control device 30 corrects the target temperature difference ⁇ T_t set in step S2. Specifically, when the water inlet temperature T wi output from the second sensor 23 is the first temperature V 1 , the control device 30 is the second temperature V 2 (where V 1 > V). 2) than, so that the target temperature difference [Delta] T _t is a small value, it corrects the target temperature difference [Delta] T _t. That is, even in the target water outlet temperature T Wo_t the same, depending on the water inlet temperature T wi with different target temperature difference [Delta] T _t, than when the water inlet temperature T wi is large is small, the target temperature difference Let ⁇ T_t be a small value.
  • FIG. 4 is an example of a relationship diagram between the water inlet temperature and the target temperature difference of the heat pump water heater according to the first embodiment. 4, as the larger the water inlet temperature T wi target temperature difference [Delta] T _t decreases, shows an example of varying the correction value of the target temperature difference [Delta] T _t stepwise.
  • the threshold value of the water inlet temperature T wi advance one determined, when the water inlet temperature T wi exceeds the threshold value, subtracting a predetermined correction value from the target temperature difference [Delta] T _t
  • the target temperature difference ⁇ T_t may be corrected.
  • FIG. 5 is another example of a relationship diagram between the water inlet temperature and the target temperature difference of the heat pump water heater according to the first embodiment.
  • the correction of the target temperature difference [Delta] T _t in addition to the water inlet temperature T wi, may be adjusted to the correction value in accordance with the ambient temperature T a.
  • the higher the ambient temperature T a is less heat radiation amount of water in the hot water supply circuit 20. Therefore, when the outside air temperature T a is greater by reducing the target temperature difference [Delta] T _t, it is possible to obtain a desired water outlet temperature T wo.
  • the control device 30 determines that the temperature difference ⁇ T between the discharged refrigerant temperature T ro detected by the first sensor 17 and the water outlet temperature T wo detected by the third sensor 24 becomes the target temperature difference ⁇ T_t corrected in step S3.
  • the opening degree of the expansion valve 13 is controlled so as to approach.
  • Step S4 the pump 22 operates to allow water from the lower portion of the tank 21 to pass through the water flow path 12b of the first heat exchanger 12, and in the process, the water is heated by the refrigerant and heated.
  • the water is returned from the upper part of the tank 21 into the tank 21. In this way, the hot water boiled in the tank 21 is stored.
  • 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 Two_t . Since the opening degree of the expansion valve 13 is controlled so that the target temperature difference ⁇ T_t is obtained in step S4, that is, the heating capacity in the heat pump cycle is maintained constant, the water speed is adjusted by adjusting the rotation speed of the pump 22. The outlet temperature Two can be ensured.
  • step S5 The control device 30 continuously performs the process of step S4 until the boiling is completed.
  • the controller 30 determines that the boiling is completed and ends the operation.
  • the opening degree of the expansion valve 13 is controlled so that the difference between the temperature difference ⁇ T between the discharge refrigerant temperature Tro and the water outlet temperature Two and the target temperature difference ⁇ T_t becomes small. Is done.
  • the value of the target temperature difference ⁇ T_t is set to be smaller when the water inlet temperature T wi is the first temperature than when the second temperature is smaller than the first temperature. Is done. For this reason, when the water inlet temperature T wi is high, the opening degree of the expansion valve 13 is controlled so that the degree of superheat of carbon dioxide, which is a refrigerant, is lower than when the water inlet temperature T wi is low. The amount of liquid refrigerant increases.
  • the control device 30 temporarily stops the hot water supply operation when the refrigerant pressure on the high pressure side exceeds the upper limit value determined at the time of design, but according to the present embodiment, an excessive increase in the refrigerant pressure is suppressed.
  • the first value of the present invention corresponds to the temperature difference ⁇ T in the present embodiment.
  • Embodiment 2 a modified example of the first embodiment will be described.
  • the control of the minimum value of the target temperature difference [Delta] T _t corrected explain.
  • the present embodiment is realized by adding a configuration to the first embodiment, and the following description will focus on differences from the first embodiment.
  • FIG. 6 is a configuration diagram of the accumulator according to the second embodiment.
  • the piping of the refrigerant circuit 10 is inserted in the upper part and the lower part of the accumulator 15, respectively, the refrigerant flows into the accumulator 15 from the upper pipe, and the gas refrigerant flows out from the lower pipe. It is a configuration. As shown in FIG. 1, the refrigerant flowing out of the accumulator 15 is sucked into the compressor 11.
  • the accumulator 15 is provided with a liquid level gauge 19 for detecting the liquid level of the liquid refrigerant in the accumulator 15.
  • the liquid level gauge 19 is not particularly limited in its specific configuration as long as it has a function of detecting the liquid level of the liquid refrigerant.
  • any type such as a magnet float type, a capacitance type, and an ultrasonic type may be used. Can be used.
  • FIG. 7 is a functional block diagram of the heat pump water heater according to the second embodiment. As shown in FIG. 7, the liquid level gauge 19 is communicably connected to the control device 30, and an output from the liquid level gauge 19 is input to the control device 30.
  • Operation control regarding the heating capability of water in the refrigerant circuit 10 of the heat pump water heater 100 is performed in the same manner as that shown in FIG. That is, the target temperature difference [Delta] T _t between the discharge refrigerant temperature Tro and the target water outlet temperature T Wo_t is corrected based on the water inlet temperature T wi. Then, the temperature difference [Delta] T between the detected discharge refrigerant temperature T ro water outlet temperature T wo is, so that the target temperature difference [Delta] T _t the corrected opening degree of the expansion valve 13 is controlled.
  • the threshold liquid level in the accumulator 15 by the level gauge 19 Is detected, the downward correction of the target temperature difference ⁇ T_t is not performed. That is, when the level gauge 19 detects a threshold value, the control device 30 maintains the current value of the target temperature difference ⁇ T_t at a current value or a value larger than the current value regardless of the detected value of the water inlet temperature T wi. To do.
  • the control device 30 performs the correction to decrease the target temperature difference ⁇ T_t as the water inlet temperature T wi is higher.
  • the increase in the pressure of the refrigerant discharged from the compressor 11 can be suppressed.
  • the control device 30 does not perform correction for reducing the target temperature difference ⁇ T_t, and therefore, it is possible to prevent an insufficient amount of refrigerant circulating in the refrigerant circuit 10.

Abstract

La présente invention concerne un distributeur d'eau chaude à pompe à chaleur qui comporte un circuit d'eau chaude et un circuit de réfrigérant dans lequel du dioxyde de carbone circule, et qui est configuré de sorte qu'un échange de chaleur se produise entre l'eau s'écoulant à travers le circuit d'eau chaude et le dioxyde de carbone s'écoulant à travers le circuit de réfrigérant dans un premier échangeur de chaleur, le circuit de réfrigérant comportant un compresseur, un canal d'écoulement de réfrigérant pour le premier échangeur de chaleur, un détendeur, et un deuxième échangeur de chaleur ; le circuit d'eau chaude comporte une cuve et un canal d'eau pour le premier échangeur de chaleur ; le distributeur d'eau chaude à pompe à chaleur est pourvu d'un premier capteur pour détecter la température du dioxyde de carbone déchargé par le compresseur, un deuxième capteur pour détecter la température de l'eau s'écoulant dans le canal d'eau du premier échangeur de chaleur, et un troisième capteur pour détecter la température de l'eau s'écoulant hors du canal d'eau du premier échangeur de chaleur ; l'angle d'ouverture du détendeur est défini de façon à amener la différence entre une première valeur et une valeur cible a diminué, la première valeur étant la différence entre une valeur de détection du troisième capteur et une valeur de détection du premier capteur, dans le cas où la valeur de détection du deuxième capteur est une première température, la valeur cible est inférieure à une deuxième température qui est inférieure à la première température.
PCT/JP2016/058439 2016-03-17 2016-03-17 Distributeur d'eau chaude à pompe à chaleur WO2017158782A1 (fr)

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JP2018505157A JP6537703B2 (ja) 2016-03-17 2016-03-17 ヒートポンプ給湯機
PCT/JP2016/058439 WO2017158782A1 (fr) 2016-03-17 2016-03-17 Distributeur d'eau chaude à pompe à chaleur
EP16894400.7A EP3431896B1 (fr) 2016-03-17 2016-03-17 Distributeur d'eau chaude à pompe à chaleur

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CN108800562A (zh) * 2018-06-20 2018-11-13 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
CN109826781A (zh) * 2018-12-28 2019-05-31 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
CN113325028A (zh) * 2021-06-07 2021-08-31 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
CN113483385A (zh) * 2021-07-02 2021-10-08 青岛海信日立空调系统有限公司 一种空气源热泵机组
WO2023273291A1 (fr) * 2021-06-28 2023-01-05 珠海格力电器股份有限公司 Procédé et appareil de commande pour système de compression et chauffe-eau à pompe à chaleur à énergie pneumatique

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Publication number Priority date Publication date Assignee Title
CN108800562A (zh) * 2018-06-20 2018-11-13 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
CN109826781A (zh) * 2018-12-28 2019-05-31 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
CN113325028A (zh) * 2021-06-07 2021-08-31 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
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
WO2023273291A1 (fr) * 2021-06-28 2023-01-05 珠海格力电器股份有限公司 Procédé et appareil de commande pour système de compression et chauffe-eau à pompe à chaleur à énergie pneumatique
CN113483385A (zh) * 2021-07-02 2021-10-08 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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EP3431896A1 (fr) 2019-01-23
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EP3431896B1 (fr) 2019-11-06
EP3431896A4 (fr) 2019-03-27

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