EP4296594A1 - Heat pump-type heat source device - Google Patents

Heat pump-type heat source device Download PDF

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Publication number
EP4296594A1
EP4296594A1 EP21926702.8A EP21926702A EP4296594A1 EP 4296594 A1 EP4296594 A1 EP 4296594A1 EP 21926702 A EP21926702 A EP 21926702A EP 4296594 A1 EP4296594 A1 EP 4296594A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
value
temperature
compressor
correction value
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21926702.8A
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German (de)
English (en)
French (fr)
Inventor
Takahiro Okamoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toshiba Carrier Corp
Original Assignee
Toshiba Carrier Corp
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 Toshiba Carrier Corp filed Critical Toshiba Carrier Corp
Publication of EP4296594A1 publication Critical patent/EP4296594A1/en
Pending legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • Embodiments described herein relate generally to a heat pump heat source device configured to create hot water to be used for indoor heating and hot-water supply by an operation of a heat pump refrigerating cycle.
  • a heat pump heat source device configured to pump up heat from outdoor air by an operation of a heat pump refrigerating cycle and supply hot water heated by the pumped-up heat to a heat radiator for indoor heating, tank for hot water supply or the like is known.
  • the heat pump heat source device includes, as main constituent elements, a compressor, four-way valve, water heat exchanger, pressure reducer (expansion valve), evaporator (air heat exchanger), and control unit and heats water flowing through the water heat exchanger by a refrigerant discharged from the compressor.
  • Patent Literature 1 JP 3495486 B
  • the flow rate of the refrigerant flowing into the air heat exchanger is set to an optimum flow rate, and it is possible to efficiently evaporate the refrigerant in the air heat exchanger.
  • the target value of the aforementioned degree of superheat At the time of setting of the target value of the aforementioned degree of superheat, if the target value is set too high, there is a possibility of the accuracy of adjustment of the degree of superheat being lowered depending on the operational state. Further, if the target value is set too low, there is a possibility of hunting of the opening degree of the expansion valve occurring. Accordingly, it is necessary to appropriately set the target value of the degree of superheat and control the opening degree of the expansion valve.
  • Embodiments described herein aim to provide a heat pump heat source device capable of appropriately setting a target value of the degree of superheat according to the operational state and realize an improvement in the control accuracy of the opening degree of the expansion valve.
  • a heat pump heat source device includes a compressor, a water heat exchanger, an air heat exchanger, a four-way valve, an expansion valve, a first temperature sensor, a second temperature sensor, and a controller.
  • the compressor discharges a compressed refrigerant.
  • the water heat exchanger heats water flowing through a flow path included therein by the refrigerant.
  • the air heat exchanger makes the refrigerant made to carry out heat exchange in the water heat exchanger absorb heat from the outdoor air to thereby be evaporated.
  • the four-way valve guides the refrigerant discharged from the compressor to the water heat exchanger and guides the refrigerant made to carry out heat exchange in the air heat exchanger to the compressor.
  • the expansion valve decompresses the refrigerant made to carry out heat exchange in the water heat exchanger and guides the decompressed refrigerant to the air heat exchanger, and can be changed an opening degree.
  • the first temperature sensor detects a first temperature of the refrigerant guided by the four-way valve so as to be sucked into the compressor.
  • the second temperature sensor detects a second temperature of the refrigerant decompressed by the expansion valve and flowing into the air heat exchanger.
  • the controller calculates a degree of superheat of the refrigerant by subtracting the second temperature from the first temperature, and changes the opening degree of the expansion valve in such a manner that the calculated degree of superheat becomes a target value.
  • the controller corrects the target value by using a first correction value varying according to heat exchange at the time of passage of the refrigerant discharged from the compressor and the refrigerant to be sucked into the compressor through the four-way valve.
  • Embodiments of the present invention will be described below with reference to FIGS. 1 to 5 .
  • FIG. 1 is a block diagram schematically showing the configurations of a heat pump hot water supply device HP including a heat pump heat source device according to this embodiment.
  • the heat pump hot water supply device HP is a device configured to create hot water by an operation of a heat pump refrigerating cycle and utilize the hot water for indoor heating and the like.
  • the heat pump hot water supply device HP includes an outdoor unit A to be generally installed outdoors, water heat exchanging unit B to be installed indoors, load unit C to be installed in a room to be air-conditioned or at a vacant space inside a building, and control unit D.
  • the heat pump heat source device is a device including a configuration formed by excluding a hot water supply tank 13, heat radiating coil (water heat radiator) 14, heater 15, heat radiators 21, 22, and 23, and tank water temperature sensor 36 from the constituent elements of the heat pump hot water supply device HP to be described later.
  • the heat pump heat source device is constituted of the outdoor unit A and water heat exchanging unit B.
  • the outdoor unit A and water heat exchanging unit B are piping-connected to each other, whereby a refrigerant is circulated through the piping, and water heat exchanging unit B and load unit C are piping-connected to each other, whereby water (hot water) is circulated through the piping.
  • Flows of the refrigerant and water (hot water) are controlled by the control unit D.
  • the outdoor unit A includes, as main constituent elements, a compressor 1, four-way valve 2, expansion valve 4, air heat exchanger 5, and accumulator 6.
  • the water heat exchanging unit B includes, as main constituent elements, a water heat exchanger 3 and circulating pump 11. Regarding the compressor 1, a rotational speed thereof is variable-speed-controlled by an inverter not shown.
  • the four-way valve 2 guides the refrigerant discharged from the compressor 1 to the water heat exchanger 3 and guides the refrigerant made to carry out heat exchange in the air heat exchanger 5 to the compressor 1.
  • one end of a refrigerant flow path of the water heat exchanger 3 is piping-connected through the four-way valve 2, and the other end of the refrigerant flow path is piping-connected to one end of the air heat exchanger 5 through the expansion valve 4 serving as a pressure reducer. Further, the other end of the air heat exchanger 5 is piping-connected to the suction port of the compressor 1 through the four-way valve 2 and accumulator 6. By these piping connections, the heat pump refrigerating cycle is formed.
  • the expansion valve 4 is, as an example, a pulse motor valve (PMV) an opening degree of which continuously changes according to the number of input drive pulses, and the opening degree thereof is controlled by a controller 40 of the control unit D to be described later between the minimum opening degree and maximum opening degree.
  • PMV pulse motor valve
  • the opening-degree-controlled expansion valve 4 decompresses the refrigerant made to carry out heat exchange in the water heat exchanger 3 and guides the decompressed refrigerant to the air heat exchanger 5.
  • an outdoor fan 7 In the vicinity of the air heat exchanger 5, an outdoor fan 7 is arranged.
  • the outdoor fan 7 sucks outdoor air and passes the sucked air through the air heat exchanger 5.
  • an outdoor air temperature sensor 30 On the upstream side of a suction-airflow-path formed by the outdoor fan 7, an outdoor air temperature sensor 30 is arranged.
  • the outdoor air temperature sensor 30 detects the temperature of the outdoor air sucked by the outdoor fan 7.
  • the gaseous refrigerant sucked into the compressor 1 is compressed by the compressor 1 and is discharged therefrom.
  • a temperature sensor first temperature sensor, hereinafter referred to as a suction refrigerant temperature sensor
  • the suction refrigerant temperature sensor 31 detects the temperature (first temperature) of the gaseous refrigerant guided by the four-way valve 2 and sucked into the compressor 1, i.e., the temperature (hereinafter referred to as the suction refrigerant temperature TS) of the gaseous refrigerant immediately before being sucked into the compressor 1.
  • the compressed gaseous refrigerant discharged from the compressor 1 flows through the refrigerant flow path of the water heat exchanger 3 by way of the four-way valve 2.
  • the gaseous refrigerant When flowing through the refrigerant flow path of the water heat exchanger 3, the gaseous refrigerant is deprived of heat thereof by the water flowing through the water flow path of the water heat exchanger 3 and is thereby condensed. That is, the water heat exchanger 3 heats the water flowing through the refrigerant flow path internally included in the water heat exchanger 3 by means of the gaseous refrigerant.
  • the liquid refrigerant flowing out of the refrigerant flow path of the water heat exchanger 3 is decompressed by the expansion valve 4 and flows through the air heat exchanger 5.
  • a temperature sensor (second temperature sensor, hereinafter referred to as the entrance refrigerant temperature sensor) 32 is attached to the piping extending from the expansion valve 4 to the air heat exchanger 5.
  • the entrance refrigerant temperature sensor 32 detects the temperature (second temperature, hereinafter referred to as the entrance refrigerant temperature TE) of the liquid refrigerant decompressed by the expansion valve 4 and flowing into the air heat exchanger 5.
  • the liquid refrigerant flowing through the air heat exchanger 5 pumps up heat from the outdoor air and is thereby evaporated. That is, the air heat exchanger 5 makes the liquid refrigerant made to carry out heat exchange by the water heat exchanger 3 absorb heat from the outdoor air to thereby evaporate.
  • the gaseous refrigerant flowing out of the air heat exchanger 5 is sucked into the compressor 1 through the four-way valve 2 and accumulator 6.
  • a temperature sensor (third temperature sensor, hereinafter referred to as the exit refrigerant temperature sensor) 33 is attached to the piping extending from the air heat exchanger 5 to the four-way valve 2.
  • the exit refrigerant temperature sensor 33 detects the temperature (third temperature, hereinafter referred to as the exit refrigerant temperature TX) of the gaseous refrigerant flowing out of the air heat exchanger 5 and flowing to the four-way valve 2.
  • the water heat exchanger 3 functions as a condenser
  • air heat exchanger 5 functions as an evaporator
  • the compressed high-temperature gaseous refrigerant discharged from the compressor 1 flows from the four-way valve 2 through the refrigerant flow path of the air heat exchanger 5 by switching of the flow path carried out by the four-way valve 2. Owing to flowing of the high-temperature gaseous refrigerant, the temperature of the air heat exchanger 5 becomes high and defrosting is thereby carried out. At the time of defrosting, the air heat exchanger 5 functions as a condenser and water heat exchanger 3 functions as an evaporator.
  • An outlet port of the water flow path of the water heat exchanger 3 is piping-connected to a suction opening of the circulating pump 11, and discharge opening of the circulating pump 11 is piping-connected to a water inlet port 12a of a three-way valve 12. Further, a water outlet port 12b of the three-way valve 12 is piping-connected to a water inflow port of the heat radiating coil (water heat radiator) 14 accommodated in the hot water supply tank 13, and water outflow port of the heat radiating coil 14 is piping-connected to an inlet port of the water flow path of the water heat exchanger 3.
  • a water outlet port 12c of the three-way valve 12 is connected to a water inlet port of each of a plurality of heat radiators 21, 22, and 23 for indoor heating, i.e., so-called fan-coil units, and water outlet port of each of the heat radiators 21, 22, and 23 is piping-connected to the inlet port of the water flow path of the water heat exchanger 3.
  • the heat radiators 21, 22, and 23 are each installed in rooms to be heated.
  • the heat radiators 21, 22, and 23 may also be floor heating appliances.
  • the circulating pump 11 sends out hot water flowing out of the water heat exchanger 3 to the hot water supply tank 13 or to the heat radiators 21, 22, and 23, and makes the water returning from the hot water supply tank 13 or from the heat radiators 21, 22, and 23 flow into the water heat exchanger 3.
  • the three-way valve 12 is an electromagnetic valve including the water inlet port 12a and two water outlet ports 12b and 12c, and configured to switch the internal flow path thereof to one of a first flow path leading from the water inlet port 12a to the water outlet port 12b and second flow path leading from the water inlet port 12a to the water outlet port 12c.
  • the water inlet port 12a is connected to the water outlet port 12c by the control unit D to be described later, and the hot water sent out of the circulating pump 11 is supplied to the heat radiators 21, 22, and 23.
  • the water inlet port 12a is connected to the water outlet port 12b, and the hot water sent out of the circulating pump 11 is supplied to the heat radiating coil 14 inside the hot water supply tank 13.
  • the entrance water temperature sensor 34 is arranged inside the water heat exchanging unit B. The entrance water temperature sensor 34 detects the temperature of the water flowing out of the hot water supply tank 13 and heat radiators 21, 22, and 23 and flowing into the water flow path of the water heat exchanger 3.
  • an exit water temperature sensor 35 is attached to the piping leading from the water heat exchanger 3 to the hot water supply tank 13 or to the heat radiators 21, 22, and 23, an exit water temperature sensor 35 is attached.
  • the exit water temperature sensor 35 is arranged on the piping between the water heat exchanger 3 and circulating pump 11. The exit water temperature sensor 35 detects the temperature of the hot water flowing out of the water heat exchanger 3 and sent to the hot water supply tank 13 or to the heat radiators 21, 22, and 23.
  • the hot water supply tank 13 incorporates therein the heat radiating coil 14 and heater (electric heater) 15, heats the water flowing into the tank 13 from a water inflow pipe 16 by heat radiation of the heat radiating coil 14 and heat generation of the heater 15, stores the heated water therein as hot water for hot-water supply, and guides the stored hot water to a water outflow pipe 17.
  • the heat radiating coil 14 makes the hot water flowing out of the water heat exchanger 3 flow from the water current inlet port to the water current outlet port while making the hot water release heat to the water (hot water) stored inside the hot water supply tank 13.
  • a faucet (tap) 17a at the tip end of the water outflow pipe 17 is opened, the hot water stored inside the hot water supply tank 13 flows out of the tank 13 through the water outflow pipe 17.
  • a tank water temperature sensor 36 is arranged inside the hot water supply tank 13. The tank water temperature sensor 36 detects the temperature of the water stored inside the hot water supply tank 13.
  • the compressor 1, four-way valve 2, expansion valve 4, air heat exchanger 5, accumulator 6, outdoor fan 7, outdoor air temperature sensor 30, suction refrigerant temperature sensor 31, entrance refrigerant temperature sensor 32, and exit refrigerant temperature sensor 33 are included in the constituent elements of the outdoor unit A.
  • the water heat exchanger 3, circulating pump 11, entrance water temperature sensor 34, and exit water temperature sensor 35 are included in the constituent elements of the water heat exchanging unit B.
  • the hot water supply tank 13, heat radiating coil 14, heater 15, heat radiators 21, 22, and 23, and three-way valve 12 are included in the constituent elements of the load unit C.
  • the manner in which the units A, B, and C include the aforementioned constituent elements is not limited to the above.
  • the control unit D controls the operations of the outdoor unit A, water heat exchanging unit B, and load unit C, circulates the refrigerant between the outdoor unit A and water heat exchanging unit B, and circulates the hot water between the water heat exchanging unit B and load unit C.
  • the control unit D includes the controller 40 and an operation display unit 41. The control unit D is installed indoors similarly to the load unit C.
  • the controller 40 is electrically connected to each of the outdoor unit A, water heat exchanging unit B, load unit C, and operation display unit 41.
  • the controller 40 includes a CPU, memory, storage device (nonvolatile memory), input/output circuit, timer, and the like and executes predetermined arithmetic processing.
  • the controller 40 reads various data items by the input/output circuit, carries out arithmetic processing by means of the CPU by using programs read from the storage device into the memory, and carries out operation control of the outdoor unit A, water heat exchanging unit B, and load unit C on the basis of the processing result.
  • the controller 40 corresponds to a control part configured to control the rotational speed of the compressor 1 and opening degree of the expansion valve 4. That is, the controller 40 successively carries out transmission/reception of control data concerning the rotational speed to/from the compressor 1 and control data concerning the opening degree to/from the expansion valve 4.
  • the operation display unit 41 is a remote control interface unit by which the user carries out setting of an operational condition to the heat pump hot water supply device HP.
  • the operation display unit 41 includes, for example, a start/stop button configured to instruct to start or stop the operation of the heat pump hot water supply device HP, manual operation buttons for the setting temperature of hot water to be supplied (hot-water supply temperature) or indoor setting temperature at the time of indoor heating, manual operation button configured to specify the operation mode of the circulating pump 11, display unit for notification of the operating status of the heat pump hot water supply device HP, and the like.
  • the operation display unit 41 is installed on the usage side such as each of supply destinations of the hot water, each of rooms which are spaces to be air-conditioned, and the like, the installation locations are not limited to these.
  • the operation display unit 41 and controller 40 may be accommodated in an integral housing or the unit 41 and controller 40 may also be accommodated in separate housings so as to be installed at different positions. It is a generally held view that the operation display unit 41 and controller 40 are installed in the vicinities of the hot water supply tank 13.
  • the arrangement of these members is not limited to the above and is arbitrary.
  • control parts each configured to separately control the operations of the outdoor unit A, water heat exchanging unit B, and load unit C may respectively be installed in the units A, B, and C. These control parts are electrically connected to each other, and carry out transmission/reception of control data to/from each other as the need arises.
  • the operation and function of the heat pump hot water supply device HP at the time of a heating operation will be described below according to the control flow of the controller 40 for each of the outdoor unit A, water heat exchanging unit B, and load unit C.
  • FIG. 2 the control flow of the controller 40 at the time of a heating operation is shown. It should be noted that although indoor heating operation control of the heat pump hot water supply device HP at the time of indoor heating is also executed by the controller 40, this is not the main subject of this embodiment, and hence a description thereof is omitted.
  • the heating operation for fully boiling the water (hot water) stored in the hot water supply tank 13 is started by, for example, the user by operating the start/stop button of the operation display unit 41.
  • the user operates the start/stop button at the time of installation of the device HP to start the operation thereof, and thereafter never stops the operation except for the case where the user is absent for a long period.
  • thermo-on condition is a condition for determining whether or not it is necessary to fully boil the water (hot water) stored in the hot water supply tank 13 when an instruction to start the heating operation is issued. According to the result (success/failure) of the thermo-on condition, it is determined whether or not the circulating pump 11 and compressor 1 should be activated. More specifically, it determined, as the thermo-on condition, whether or not the tank water temperature of the hot water supply tank 13 is lower than or equal to the thermo-on water temperature.
  • the thermo-on water temperature is a temperature requiring boiling of the hot water stored in the hot water supply tank 13 and is, for example, a value obtained by subtracting a predetermined value (as an example, 20°C) from the hot water supply temperature (thermo-off temperature to be described later) which is the tank water temperature set by the user by operating the manual operation button of the operation display unit 41.
  • the value of the thermo-on water temperature is retained in, for example, the storage device of the controller 40 and is read therefrom into the memory and is used as the parameter at the time of determination of the thermo-on condition.
  • the controller 40 acquires the tank water temperature from the tank water temperature sensor 36, and compares the tank water temperature with the thermo-on water temperature.
  • the controller 40 considers that it is necessary to fully boil the hot water stored in the hot water supply tank 13, and thereby determines that the thermo-on condition is established.
  • the controller 40 considers that it is not necessary to fully boil the hot water stored in the hot water supply tank 13, and thereby determines that the thermo-on condition is not established.
  • the controller 40 repeats the determination of the thermo-on condition until the thermo-on condition is established. At this time, the controller 40 may execute predetermined failure processing.
  • the failure processing is, for example, waiting processing of waiting for determination of the thermo-on condition for a predetermined time, timeout processing or retry processing of terminating the heating operation in the case where the thermo-on condition is not established even when determination thereof is repeated for a predetermined time or is repeated a predetermined number of times, processing formed by combining these together, and the like.
  • the controller 40 activates the circulating pump 11 (S102). Thereby, the hot water starts circulation between the water heat exchanging unit B and hot water supply tank 13 (more specifically, heat radiating coil 14).
  • the hot water circulating between the water heat exchanging unit B and hot water supply tank 13 as described above is referred to as circulating water.
  • the controller 40 switches the internal flow path of the three-way valve 12 to the first flow path leading from the water inlet port 12a to the water outlet port 12b.
  • the controller 40 activates the compressor 1 (S103).
  • the controller 40 controls the four-way valve 2 to make the refrigerant discharged from the compressor 1 circulate through the path formed by way of the water heat exchanger 3, expansion valve 4, air heat exchanger 5, four-way valve 2, and accumulator 6 in sequence in the order mentioned and return to the compressor 1 while making the refrigerant make vapor-liquid phase transition.
  • the hot water (circulating water) circulating between the water heat exchanging unit B and hot water supply tank 13 is heated by the gaseous refrigerant discharged from the compressor 1 while flowing through the water heat exchanger 3, and the water temperature thereof is raised.
  • the aforementioned hot water releases heat inside the hot water supply tank 13 while the hot water flows through the heat radiating coil 14.
  • the tank water temperature of the hot water supply tank 13 is raised.
  • the controller 40 acquires the temperature of the refrigerant at predetermined positions of the outdoor unit A.
  • the controller 40 acquires the value of each of the suction refrigerant temperature TS, entrance refrigerant temperature TE, and exit refrigerant temperature TX (S104).
  • the controller 40 acquires the detection values of the suction refrigerant temperature TS, entrance refrigerant temperature TE, and exit refrigerant temperature TX respectively from the suction refrigerant temperature sensor 31, entrance refrigerant temperature sensor 32, and exit refrigerant temperature sensor 33.
  • the controller 40 sets a target value (target degree of superheat) SH0 at the time of controlling the degree of superheat SH of the refrigerant (S105).
  • the value of the degree of superheat SH is a value to be calculated as a temperature difference (TS-TE) between the suction refrigerant temperature TS and entrance refrigerant temperature TE.
  • the controller 40 refers to Table T3 shown in FIG. 3 .
  • Table T3 is stored in, for example, the storage device of the controller 40.
  • the controller 40 reads a desired value recorded in Table T3 into the memory, and sets the target value SH0 according to the aforementioned value.
  • the set target value SH0 is retained in, for example, the memory of the controller 40 and is read therefrom as a parameter at the time (S111, S113) of determination of the opening degree change condition to be described later.
  • the rotational speed Hz of the compressor 1 is controlled by changing the output of the inverter according to, for example, a difference between the temperature of the hot water to be produced (temperature to be detected by the exit water temperature sensor 35) and hot water supply setting temperature, water temperature difference between the entrance and exit of the water heat exchanger 3 (detection temperature difference between the exit water temperature sensor 35 and entrance water temperature sensor 34), difference between the room temperature of the room in which the heat radiator 21, 22, or 23 through which the hot water is made to flow is installed and setting room temperature, difference between the water temperature of the hot water supply tank 13 (temperature to be detected by the tank water temperature sensor 36) and hot water supply tank hot water supply setting temperature, or combinations of these, or by incorporation of Proportional Integral Differential (PID) control of each value.
  • PID Proportional Integral Differential
  • the reference value SHV is the heat exchange amount (temperature change) of the refrigerant in the air heat exchanger 5, and is a constant value. Although in the example shown in FIG. 3 , the reference value SHV is made 2, the reference value SHV is not limited to this and is freely settable.
  • the first correction value X1 is a correction value in which the increment in the degree of superheat in the four-way valve 2 is taken into account, and varies according to the heat exchange to be made when the refrigerant discharged from the compressor 1 and refrigerant to be sucked into the compressor 1 pass through the four-way valve 2.
  • the first correction value X1 is the temperature difference (TS-TX) between the suction refrigerant temperature TS and exit refrigerant temperature TX, i.e., a value calculated by subtracting the exit refrigerant temperature TX from the suction refrigerant temperature TS.
  • the second correction value X2 is a correction value in the pressure loss of the refrigerant in the air heat exchanger 5 is taken into account, and is a value of a variable set in advance according to the rotational speed Hz of the compressor 1.
  • the rotational speed Hz of the compressor 1 is classified by four thresholds.
  • a threshold Z1 is a first threshold
  • Z2 is a second threshold
  • Z3 is a third threshold
  • Z4 is a fourth threshold.
  • Z1 is the minimum value
  • Z2 and Z3 become greater in sequence
  • Z4 is the maximum value.
  • the fourth threshold Z4 is the value of the maximum rotational speed of compressor 1 within the allowable operation range.
  • the controller 40 calculates the target value SH0 according to which of the four ranges partitioned with the first to fourth thresholds Z1 to Z4 the rotational speed Hz of the compressor 1 corresponds to. It should be noted that the number of the thresholds may also be less than or equal to three or may be greater than or equal to five.
  • the second correction value X2 when the rotational speed Hz of the compressor 1 is less than or equal to Z1 (hereinafter referred to as being within the first range), the second correction value X2 is 0.
  • the second correction value X2 is 1.
  • the second correction value X2 is 2.
  • the second correction value X2 is 3.
  • 21 is 30 Hz
  • Z2 is 45 Hz
  • Z3 is 60 Hz
  • Z4 is 90 Hz (maximum value).
  • TS-TX temperature difference
  • the target value SH0 is set by correcting the reference value SHV which is the heat exchange amount of the refrigerant in the air heat exchanger 5 while taking each of the first correction value X1 indicating the increment in the degree of superheat SH in the four-way valve 2 and second correction value X2 indicating the pressure loss of the refrigerant in the air heat exchanger 5 into account.
  • the controller 40 sets the target value SH0 to a value (2+X1) obtained by adding 2 to the first correction value X1.
  • the controller 40 sets the target value SH0 to a value (1+X1) obtained by adding 1 to the first correction value X1.
  • the controller 40 sets the target value SH0 to a value of the first correction value X1.
  • the controller sets the target value SH0 to a value (-1+X1) obtained by subtracting 1 from the first correction value X1.
  • the controller 40 Upon completion of setting of the target value SH0, the controller 40 starts control of the opening degree of the expansion valve 4 in such a manner that the degree of superheat SH becomes the set target value SH0 (S106). From another point of view, the controller 40 changes the opening degree of the expansion valve 4 in such a manner that the temperature difference between the exit refrigerant temperature TX and entrance refrigerant temperature TE becomes the reference value SHV. Thereby, in the heat pump hot water supply device HP, opening degree control of the expansion valve 4 is started in order to make the value of the degree of superheat SH of the refrigerant, i.e., the temperature difference (TS-TE) between the suction refrigerant temperature TS and entrance refrigerant temperature TE the target value SH0.
  • TS-TE temperature difference
  • the controller 40 determines the thermo-off condition (S107). According to success/failure of the thermo-off condition, the controller 40 determines whether or not the opening degree control of the expansion valve 4 should be continued.
  • the thermo-off condition is a condition for determining whether or not it has become unnecessary to boil the hot water stored in the hot water supply tank 13. According to success/failure of the thermo-off condition, it is determined whether or not the circulating pump 11 and compressor 1 should be stopped.
  • thermo-off condition when one of the first thermo-off condition and second thermo-off condition is established, the thermo-off condition is established and the compressor 1 is stopped and, when neither of the first thermo-off condition and second thermo-off condition is established, the thermo-off condition is not established, and the operations of the circulating pump 11 and compressor 1 are continued.
  • thermo-off water temperature is a temperature not requiring further heating (boiling) of the hot water stored in the hot water supply tank 13 and is, for example, a hot water supply temperature set by the user by operating the manual operation button of the operation display unit 41.
  • the value of the thermo-off water temperature is retained in, for example, the memory of the controller 40, and is used as a parameter at the time of determination of the first thermo-off condition.
  • the controller 40 acquires the tank water temperature from the tank water temperature sensor 36, and compares the acquired tank water temperature with the thermo-off water temperature.
  • the controller 40 considers that it has become unnecessary to boil the hot water stored in the hot water supply tank 13, and thereby determines that the thermo-off condition is established.
  • the controller considers that it is necessary to further boil the hot water stored in the hot water supply tank 13, and determines that the first thermo-off condition is not established.
  • the protection temperature is set in order to prevent the suction refrigerant temperature TS from becoming excessively high and protect the compressor 1, and is the temperature of the upper limit of the hot water (circulating water) allowed to flow into the water heat exchanger 3.
  • the protection temperature is the temperature of the upper limit of the circulating water carrying out heat exchange with the high-temperature gaseous refrigerant and is set in advance according to, for example, the performance or the like of the compressor 1.
  • the value of the protection temperature is retained in, for example, the storage device of the controller 40 and is read therefrom into the memory to be used as a parameter at the time of determination of the second thermo-off condition.
  • the controller 40 acquires the entrance water temperature from the entrance water temperature sensor 34 and compares the acquired entrance water temperature with the protection temperature (for example, 54°C). In this embodiment, as an example, when the entrance water temperature is higher than or equal to the protection temperature, the controller 40 determines that the second thermo-off condition is established. In this case, it is considered that the situation requires stoppage so that the allowable operation range of the compressor 1 is not exceeded, and the second thermo-off condition is considered to be established. Thereby, protection of the compressor 1 is attained. On the other hand, when the entrance water temperature is lower than the protection temperature, the controller 40 determines that the second thermo-off condition is not established.
  • the protection temperature for example, 54°C.
  • thermo-off condition When the thermo-off condition is established by these first thermo-off condition and second thermo-off condition, the controller 40 stops the compressor 1 (S108) .
  • the controller 40 resets the correction value SHX of the target value SH0 to the initial value (S109).
  • the initial value of the correction value SHX is, for example, 0 (zero) and in this case, the controller 40 clears the correction value SHX to zero. That is, each of the first correction value X1 and second correction value X2 is cleared to zero. Thereby, the opening degree control of the expansion valve 4 in the heat pump hot water supply device HP is terminated.
  • the controller 40 stops the circulating pump 11 (S110). Thereby the heating operation of the heat pump hot water supply device HP is terminated.
  • the opening degree change condition is a condition for determining to which of raising, lowering, and maintenance the opening degree of the expansion valve 4 should be made to make transition. According to success/failure of the opening degree change condition, it is determined to which of rising, lowering, and maintenance the opening degree of the expansion valve 4 should be made to make transition.
  • each of the first opening degree change condition and second opening degree change condition is determined.
  • the opening degree of the expansion valve 4 When the first opening degree change condition is established, the opening degree of the expansion valve 4 is raised and, when the second opening degree change condition is established, the opening degree of the expansion valve 4 is lowered. When neither of the first and second opening degree change conditions is established, the opening degree of the expansion valve 4 is maintained.
  • the first opening degree change condition is a condition for determining whether or not the degree of superheat SH exceeds the target value SH0. According to success/failure of the first opening degree change condition, it is determined whether or not the opening degree of the expansion valve 4 should be raised.
  • the controller 40 acquires the suction refrigerant temperature TS from the suction refrigerant temperature sensor 31, acquires the entrance refrigerant temperature TE from the entrance refrigerant temperature sensor 32, and calculates the degree of superheat SH as the temperature difference (TS-TE) between the acquired temperatures.
  • the controller 40 reads the target value SH0 retained in the memory and compares the target value SH0 with the calculated value of the degree of superheat SH. When the degree of superheat SH exceeds the target value SH0, the controller 40 determines that the first opening degree change condition is established. On the other hand, when the degree of superheat SH does not exceed the target value SH0 (less than or equal to SH0), the controller 40 determines that the first opening degree change condition is not established.
  • the controller 40 raises the opening degree of the expansion valve 4 (S112).
  • the opening degree of the expansion valve 4 is raised, the flow rate of the refrigerant flowing into the air heat exchanger 5 is increased. Meanwhile, the amount of heat pumped up from the outdoor air is not changed, thus the suction refrigerant temperature TS is lowered, and the temperature difference between the temperature TS and entrance refrigerant temperature TE, i.e., the value of the degree of superheat SH becomes smaller.
  • the amount of a raise in the opening degree is not particularly limited and is arbitrarily settable.
  • the second opening degree change condition is a condition for determining whether or not the degree of superheat SH has reached the target value SH0. According to success/failure of the second opening degree change condition, it is determined whether or not the opening degree of the expansion valve 4 should be lowered.
  • the controller 40 calculates the value of the degree of superheat SH as the temperature difference (TS-TE) between the suction refrigerant temperature TS and entrance refrigerant temperature TE, and compares the value of the calculated degree of superheat SH with the target value SH0 read from the memory.
  • the controller 40 determines that the second opening degree change condition is established.
  • the controller 40 determines that the second opening degree change condition is not established.
  • the controller 40 lowers the opening degree of the expansion valve 4 (S114).
  • the opening degree of the expansion valve 4 is lowered, the flow rate of the refrigerant flowing into the air heat exchanger 5 is decreased. Meanwhile, the amount of heat pumped up from the outdoor air is not changed, thus the suction refrigerant temperature TS is raised, and the temperature difference between the temperature TS and entrance refrigerant temperature TE, i.e., the value of the degree of superheat SH becomes larger.
  • the amount of lowering of the opening degree is not particularly limited and is arbitrarily settable. For example, the amount of raising and amount of lowering of the opening degree may be coincident with each other or may be different from each other.
  • the amount of raising and amount of lowering of the opening degree may be fixed amounts (fixed values) irrespective of, for example, the difference between the degree of superheat SH and target value SH0 or may be variable amounts (values of variables) corresponding to the aforementioned difference.
  • the controller 40 maintains the opening degree of the expansion valve 4 (S115).
  • the degree of superheat SH and target value SH0 are coincident with each other, i.e., the degree of superheat of the refrigerant is equal to the target value, and the opening degree of the expansion valve 4 is maintained as it is without being changed. Accordingly, the flow rate of the refrigerant flowing into the air heat exchanger 5 is also maintained as it is. Thereby, the suction refrigerant temperature TS is kept, and temperature difference between the suction refrigerant temperature TS and entrance refrigerant temperature TE, i.e., the value of the degree of superheat SH is maintained.
  • the controller 40 upon making the opening degree of the expansion valve 4 make transition to one of raising, lowering, and maintenance, the controller 40 starts a timer for opening degree change in order to repeat the aforementioned change in the opening degree within a predetermined time (S116). It is sufficient if the predetermined time is set to a value most appropriate for intervals at which the opening degree of the expansion valve 4 is changed according to, for example, the operational condition or the like of the heat pump hot water supply device HP.
  • the controller 40 determines the opening degree change condition again in order to repeat the change in the opening degree of the expansion valve 4. More specifically, the controller 40 determines the first opening degree change condition (S111), and appropriately executes the processing from S112 to S116 according to success/failure of the aforementioned determination. At the aforementioned time, the controller 40 resets the counted-up timer.
  • the controller 40 determines the thermo-off condition again (S118).
  • the controller 40 determines again whether or not the predetermined time has elapsed (S117). That is, the controller 40 appropriately repeats the determination of the opening degree change condition until the thermo-off condition is established within the predetermined time. Therefore, according to success/failure of these conditions, raising, lowering, and maintenance of the opening degree of the expansion valve 4 are appropriately repeated.
  • thermo-off condition first thermo-off condition
  • compressor 1 is stopped (S108)
  • correction value SHX of the target value SH0 is reset to the initial value (S109)
  • circulating pump 11 is stopped (S110).
  • the opening degree of the expansion valve 4 is controlled in such a manner that the degree of superheat SH of the refrigerant becomes the target value SH0.
  • the target value SH0 is calculated by modifying the reference value SHV with the predetermined correction value SHX according to the rotational speed Hz of the compressor 1.
  • the first correction value X1 is the temperature difference (TS-TX) between the suction refrigerant temperature TS and exit refrigerant temperature TX and is a correction value varying in consideration of the increment in the degree of superheat SH in the four-way valve 2.
  • the second correction value X2 is the correction value in which the pressure loss of the refrigerant in the air heat exchanger 5 is taken into consideration and is the value of the variable correspondent to the rotational speed Hz of the compressor 1.
  • the target value SH0 by the first correction value X1, in other words, it is possible to correct the target value SH0 in consideration of the increment in the degree of superheat SH in the four-way valve 2.
  • the target value SH0 by the second correction value X2, in other words, it is possible to correct the target value SH0 in consideration of the pressure loss of the refrigerant in the air heat exchanger 5.
  • the target value SH0 is corrected by the first correction value X1 in which the increment in the degree of superheat SH in the four-way valve 2 is taken into account, and hence there is no need to set the target value SH0 higher in advance while taking the increment in the degree of superheat SH in the four-way valve 2 into account.
  • the opening degree of the expansion valve 4 is controlled in such a manner as to bring the degree of superheat in the air heat exchanger 5 close to 0 and bring the degree of superheat in the four-way valve 2 close to 3 by setting the target value of the degree of superheat to 3.
  • the degree of superheat in the air heat exchanger 5 is assumed to be 0, the refrigerant passes through the four-way valve 2 as it is in liquid form.
  • the liquid refrigerant is higher in density than the gaseous refrigerant and requires greater energy for heat exchange, and hence heat absorption corresponding to the amount of about 3 [K] in the four-way valve 2 is made difficult.
  • the degree of superheat becomes 0 as a whole, and the control is shifted to control of tightening of the expansion valve 4. Accordingly, in order to stabilize the control of the expansion valve 4, it is required that the target value of the degree of superheat be set to 4 or more.
  • the target value SH0 is corrected by the first correction value X1 varying in consideration of the increment in the degree of superheat SH in the four-way valve 2, and hence it is possible to avoid such a situation.
  • the amount of rise in the degree of superheat SH in the four-way valve 2 varies depending on the state of the refrigerating cycle, and hence by making, as in the case of this embodiment, the target value SH0 not a fixed value but a variable value which is a value adapted to the operational state of the heat pump hot water supply device HP, it is possible to suppress over-tightening of the expansion valve 4.
  • the setting of the target value SH0 is excessively low, there is a possibility of the opening degree of the expansion valve 4 causing hunting. It is possible to avoid the aforementioned hunting of the opening degree of the expansion valve 4 by correcting the target value SH0 by the first correction value X1 varying in consideration of the increment in the degree of superheat SH in the four-way valve 2.
  • the flow rate of the refrigerant flowing into the air heat exchanger 5 is set the optimum flow rate, and it is possible to efficiently evaporate the refrigerant in the air heat exchanger 5. Accordingly, it becomes possible to improve the heating performance of the heat pump hot water supply device HP.
  • the target value SH0 of the degree of superheat SH of the refrigerant is calculated by modifying the reference value SHV with the correction value X according to the rotational speed Hz of the compressor 1.
  • the first correction value X1 is the correction value in which the increment in the degree of superheat in the four-way valve 2 is taken into account, and is the temperature difference (TS-TX) between the suction refrigerant temperature TS and exit refrigerant temperature TX.
  • TS-TX temperature difference
  • the configuration itself of the heat pump heat source device of the second embodiment is equivalent to the configuration of the heat pump hot water supply device HP of the first embodiment shown in FIG. 1 .
  • the exit refrigerant temperature sensor 33 can be omitted and is not an indispensable constituent element.
  • FIG. 4 the control flow of a controller 40 at the time of a heating operation in this embodiment is shown.
  • control of the controller 40 at the time of the heating operation in this embodiment will be described below.
  • the control flow of the heating operation of this embodiment is formed by changing a part of the control flow ( FIG. 2 ) of the first embodiment and adding the part to the control peculiar to the second embodiment. Accordingly, control identical to the first embodiment described above is denoted by a step number identical to the first embodiment and a description thereof is omitted, and control peculiar to the second embodiment will be described in detail.
  • the controller 40 determines the thermo-on condition (S101) and, when the thermo-on condition is established, activates a circulating pump 11 (S102), and activates a compressor 1 (S103). At this time, the controller 40 repeats the determination of the thermo-on condition until the thermo-on condition is established. Further, the controller 40 starts a timer configured to measure the continuous operation time of the compressor 1.
  • the controller 40 Upon activation of the compressor 1, the controller 40 acquires the value of each of the suction refrigerant temperature TS and entrance refrigerant temperature TE (S201). At this time, the controller 40 acquires the detection value of each of the suction refrigerant temperature TS and entrance refrigerant temperature TE from each of a suction refrigerant temperature sensor 31 and entrance refrigerant temperature sensor 32.
  • the controller 40 sets the target value SH0 at the time of controlling the degree of superheat SH (S202).
  • the controller 40 refers to Table T5 shown in FIG. 5 different from Table 3 ( FIG. 3 ) of the first embodiment.
  • Table 5 is stored in, for example, the storage device of the controller 40.
  • the controller 40 reads the desired value recorded in Table 5 into the memory, and sets the target value SH0 according to the value.
  • the set target value SH0 is retained in, for example, the memory of the controller 40, and is read therefrom as a parameter at the time of determination of the opening degree change condition (S111, S113) to be described later.
  • the value of the reference value SHV is 2, this being identical to the first embodiment. It should be noted that the value of the reference value SHV is not limited to the above and is freely settable, this also being identical to the first embodiment.
  • the first correction value Y1 is a correction value taking the increment in the degree of superheat SH in the four-way valve 2 into account, varies according to the heat exchange at the time when each of the refrigerant discharged from the compressor 1 and refrigerant to be sucked into the compressor 1 passes through the four-way valve 2, and the initial value thereof is 0 (zero).
  • a predetermined value (1 as an example) is added each time the liquid return of the refrigerant from the air heat exchanger 5 to the four-way valve 2 at the time of a heating operation (or at the time of an indoor heating operation) of the heat pump hot water supply device HP is determined.
  • Addition of the first correction value Y1 at the time of the aforementioned determination of the liquid return is carried out when a change in the degree of superheat SH is monitored at the time of, for example, determination of the opening degree change condition to be described later and, in the case or the like where the degree of superheat SH turns to lowering in spite of no significant change in the rotational speed Hz of the compressor 1.
  • the aforementioned addition of the first correction value Y1 is not carried out.
  • the second correction value Y2 is, similarly to the second correction value X2 in the first embodiment, a correction value taking the pressure loss of the refrigerant in the air heat exchanger 5 into account, and is a variable value set in advance according to the rotational speed Hz of the compressor 1.
  • the rotational speed Hz of the compressor 1 is classified by the first to fourth thresholds Z1 to Z4.
  • the controller 40 calculates the target value SH0 according to which of the four ranges partitioned with the first to fourth thresholds Z1 to Z4 the rotational speed Hz of the compressor 1 corresponds to.
  • the number of the thresholds may also be less than or equal to three or may be greater than or equal to five.
  • the second correction value Y2 when the rotational speed Hz of the compressor 1 is within the first range, the second correction value Y2 is 0. When the rotational speed Hz of the compressor 1 is within the second range, the second correction value Y2 is 1. When the rotational speed Hz of the compressor 1 is within the third range, the second correction value Y2 is 2. When the rotational speed Hz of the compressor 1 is within the fourth range, the second correction value Y2 is 3.
  • the target value SH0 is set by correcting the reference value SHV which is the heat exchange amount of the refrigerant in the air heat exchanger 5 while taking each of the first correction value Y1 indicating the increment in the degree of superheat SH in the four-way valve 2 and second correction value Y2 indicating the pressure loss of the refrigerant in the air heat exchanger 5 into account.
  • the controller 40 sets the target value SH0 to a value (2+Y1) obtained by adding 2 to the first correction value Y1.
  • the controller 40 sets the target value SH0 to a value (1+Y1) obtained by adding 1 to the first correction value Y1.
  • the controller 40 sets the target value SH0 to a value of the first correction value Y1.
  • the controller sets the target value SH0 to a value (-1+Y1) obtained by subtracting 1 from the first correction value Y1.
  • the controller 40 records and retains the current values of the degree of superheat SH, entrance refrigerant temperature TE, and rotational speed Hz of the compressor 1 in the memory (S203). These retained values are read from the memory as parameters at the time (S204, S205, S206) of determination of the correction value change condition of the first correction value Y1 to be described later.
  • the value of the degree of superheat is, similarly to the first embodiment, a value calculated as a temperature difference (TS-TE) between the suction refrigerant temperature TS and entrance refrigerant temperature TE.
  • the controller 40 starts control of the opening degree of the expansion valve 4 in such a manner that value of the degree of superheat SH becomes the set target value SH0 (S106). From another point of view, the controller 40 changes the opening degree of the expansion valve 4 in such a manner that the temperature difference between the exit refrigerant temperature TX and entrance refrigerant temperature TE becomes the reference value SHV. Thereby, in the heat pump hot water supply device HP, opening degree control of the expansion valve 4 is started in order to make the value of the degree of superheat SH of the refrigerant, i.e., the temperature difference (TS-TE) between the suction refrigerant temperature TS and entrance refrigerant temperature TE the target value SH0.
  • TS-TE temperature difference
  • the controller 40 determines the thermo-off condition (S107). According to success/failure of the thermo-off condition, the controller 40 determines whether or not the opening degree control of the expansion valve 4 should be continued.
  • the controller 40 stops the compressor 1 (S108). Subsequently, the controller 40 resets the correction value SHV of the target value SH0 to the initial value (S109). In this case, the controller 40 clears the value of each of the first correction value Y1 and second correction value Y2 to zero. Thereby, the opening degree control of the expansion valve 4 in the heat pump hot water supply device HP is terminated. Subsequently, the controller 40 stops the circulating pump 11 (S110). Thereby, the heating operation of the heat pump hot water supply device HP is terminated.
  • the controller 40 determines the opening degree change condition.
  • the opening degree change condition is identical to the first embodiment, and each of a first opening degree change condition and second opening degree change condition is determined as the opening degree change condition, this also being identical to the first embodiment. Accordingly, when the first opening degree change condition is established, the opening degree of the expansion valve 4 is raised and, when the second opening degree change condition is established, the opening degree of the expansion valve 4 is lowered (Sill to S114). When neither of the first and second opening degree change conditions is established, the opening degree of the expansion valve 4 is maintained (S115).
  • the controller 40 upon making the opening degree of the expansion valve 4 make transition to one of raising, lowering, and maintenance, the controller 40 starts a timer for opening degree change in order to repeat the aforementioned change in the opening degree within a predetermined time and, furthermore, in this embodiment, in order to determine whether or not the first correction value Y1 should be changed (S116).
  • the controller 40 determines the thermo-off condition again (S118), and appropriately repeats the determination of the opening degree change condition and determination whether or not the first correction value Y1 should be changed until the thermo-off condition is established within the predetermined time. Accordingly, similarly to the first embodiment, according to success/failure of these conditions, raising, lowering, and maintenance of the opening degree of the expansion valve 4 and change of the first correction value Y1 are appropriately repeated.
  • thermo-off condition first thermo-off condition
  • the compressor 1 is stopped (S108)
  • correction value SHY of the target value SH0 is reset to the initial value (S109)
  • circulating pump 11 is stopped (S110).
  • the controller 40 determines the correction value change condition in order to determine whether or not the first correction value Y1 should be changed.
  • the correction value change condition is a condition for determining whether or not the first correction value Y1 should be changed.
  • the correction value change condition in this case is a condition for determining whether or not occurrence of liquid return of the refrigerant made to carry out heat exchange in the air heat exchanger 5 and flowing to the compressor 1 is caused. According to success/failure of the correction value change condition, it is determined whether or not a predetermined value (for example, 1) should be added one by one as the first correction value Y1.
  • each of first to fourth correction value change conditions is determined as the correction value change condition, in other words, condition for occurrence of liquid return of the refrigerant.
  • the first correction value Y1 is added and, when any one of the first to fourth correction value change conditions is not established, the first correction value Y1 is not added and the value is maintained.
  • the controller 40 When determining the correction value change condition, as an example, the controller 40 first determines the first correction value change condition (S204).
  • the first correction value change condition is a condition for determining whether or not the degree of superheat SH is lower than the degree of superheat SH at the time of the last-time condition determination by a predetermined value.
  • the predetermined value can be set to an arbitrary value, in this embodiment, as an example, the value is set to 3.
  • the controller 40 acquires the suction refrigerant temperature TS from the suction refrigerant temperature sensor 31, acquires the entrance refrigerant temperature TE from the entrance refrigerant temperature sensor 32, and calculates the degree of superheat SH (hereinafter referred to as the current degree of superheat SH) as the temperature difference (TS-TE) between these temperatures. Then, the controller 40 compares a value obtained by reading the degree of superheat SH (hereinafter referred to as the previous degree of superheat SH) retained in the memory, and subtracting the predetermined value from the read degree of superheat SH with the value of the current degree of superheat SH.
  • the degree of superheat SH hereinafter referred to as the previous degree of superheat SH
  • the value of the previous degree of superheat SH is the value, at the time of the first-time determination of the first correction value change condition, retained in the memory in S203, and is the value, at the time of each subsequent determination, retained in the memory in S209 to be described later.
  • the controller 40 determines that the first correction value change condition is established.
  • the controller 40 determines that the first correction value change condition is not established.
  • the second correction value change condition is a condition for determining whether or not the entrance refrigerant temperature TE is lower than the entrance refrigerant temperature TE at the time of the last-time condition determination by the predetermined value.
  • the predetermined value can be set to an arbitrary value, in this embodiment, as an example, the value is set to 2.
  • the controller 40 compares the value of entrance refrigerant temperature TE (hereinafter referred to as the current refrigerant temperature TE) acquired from the entrance refrigerant temperature sensor 32 with the value obtained by subtracting the predetermined value from the value of the entrance refrigerant temperature TE (hereinafter referred to as the previous entrance refrigerant temperature TE) read from the memory.
  • the value of the previous entrance refrigerant temperature TE is the value, at the time of the first-time determination of the second correction value change condition, retained in the memory in S203, and is the value, at the time of each subsequent determination, retained in the memory in S209 to be described later.
  • the controller 40 determines that the second correction value change condition is established.
  • the controller 40 determines that the second correction value change condition is not established.
  • the controller 40 determines the third correction value change condition (S206).
  • the third correction value change condition is a condition for determining whether or not a difference between the rotational speed Hz of the compressor 1 and rotational speed Hz at the time of the last-time condition determination is within a predetermined range.
  • the predetermined range can be set to an arbitrary range, in this embodiment, as an example, the range is made a range greater than or equal to -5 and less than or equal to 5.
  • the controller 40 determines whether or not a difference between the value of the rotational speed Hz (hereinafter referred to as the current rotational speed Hz) acquired from the compressor 1 and value of the rotational speed Hz (hereinafter referred to as the previous rotational speed Hz) read from the memory is within the predetermined range.
  • the value of the previous rotational speed Hz is the value, at the time of the first-time determination of the third correction value change condition, retained in the memory in S203, and is the value, at the time of each subsequent determination, retained in the memory in S209 to be described later.
  • the controller 40 determines that the third correction value change condition is established.
  • the controller 40 determines that the third correction value change condition is not established.
  • the fourth correction value change condition is a condition for determining whether or not a fixed time has elapsed from the startup of the compressor 1.
  • the fixed time is set in advance as a value of the continuous operation time required for the compressor 1 to build up the rotational speed Hz thereof from the startup to the stable operation, is retained in, for example, the storage device of the controller 40, and is read therefrom into the memory at the time of determination of the fourth correction value change condition to thereby be used as a parameter.
  • the controller 40 determines, for example, whether or not the measured value of a timer configured to measure the continuous operation time of the compressor 1 exceeds the fixed time. When the measured value exceeds the fixed time, the controller 40 determines that the fourth correction value change condition is established. On the other hand, when the measured value is less than or equal to the fixed time, the controller 40 determines that the fourth correction value change condition is not established.
  • the controller 40 adds a predetermined value (1 as an example) as the first correction value Y1 (S208).
  • the correction value change condition is established, and the first correction value Y1 is changed. That is, this case corresponds to the case where liquid return of the refrigerant made to carry out heat exchange in the air heat changer 5 and flowing to the compressor occurs, i.e., this case corresponds to the case where the refrigerant liquid return occurrence condition is established.
  • the correction value SHY is increased by 1 and, as a result, the target value SH0 is also increased by 1.
  • the controller 40 records and retains the current values of the degree of superheat SH, entrance refrigerant temperature TE, and rotational speed Hz of the compressor 1 in the memory (S209).
  • the aforementioned current values are respectively the current degree of superheat SH, current entrance refrigerant temperature TE, and current rotational speed Hz respectively used in S204, S205, and S206.
  • the retained values are read from the memory as the values of the last-time determination at the time of the next-time correction value change condition determination and are used as parameters.
  • the controller 40 determines the opening degree change condition again in order to repeat the change in the opening degree of the expansion valve. More specifically, the controller 40 determines the first opening degree change condition (S111), and appropriately executes the control from S112 to S116 according to success/failure of the aforementioned determination. At this time, the controller 40 resets the timer for opening degree change which has counted up. Further, when the first correction value change condition is not established in S204, when the second correction value change condition is not established in S205, when the third correction value change condition is not established in S206 and, also when the fourth correction value change condition is not established in S206, the controller 40 determines the opening degree change condition in the same manner again.
  • the controller 40 when the third correction value change condition is not established in S206, the controller 40 resets the first correction value Y1 of the target value SH0 to the initial value before determining the opening degree change condition again. In this case, the controller 40 once clears the value of the first correction value Y1 to zero.
  • the exit refrigerant temperature sensor 33 is not an indispensable constituent element and can be omitted. Accordingly, it is possible to reduce the procurement cost by an amount corresponding to the exit refrigerant temperature sensor 33.

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP21926702.8A 2021-02-18 2021-10-20 Heat pump-type heat source device Pending EP4296594A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021024459A JP2024045788A (ja) 2021-02-18 2021-02-18 ヒートポンプ式熱源装置
PCT/JP2021/038773 WO2022176273A1 (ja) 2021-02-18 2021-10-20 ヒートポンプ式熱源装置

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EP4296594A1 true EP4296594A1 (en) 2023-12-27

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