WO2010070842A1 - Dispositif de pompe à chaleur - Google Patents

Dispositif de pompe à chaleur Download PDF

Info

Publication number
WO2010070842A1
WO2010070842A1 PCT/JP2009/006682 JP2009006682W WO2010070842A1 WO 2010070842 A1 WO2010070842 A1 WO 2010070842A1 JP 2009006682 W JP2009006682 W JP 2009006682W WO 2010070842 A1 WO2010070842 A1 WO 2010070842A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
secondary refrigerant
heat exchanger
primary
heat
Prior art date
Application number
PCT/JP2009/006682
Other languages
English (en)
Japanese (ja)
Inventor
遠藤和広
大塚厚
井本勉
福田崇
Original Assignee
日立アプライアンス株式会社
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 日立アプライアンス株式会社 filed Critical 日立アプライアンス株式会社
Publication of WO2010070842A1 publication Critical patent/WO2010070842A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using 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
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a heat pump device, and is particularly suitable for a heat pump device including a primary refrigerant circuit and a secondary refrigerant circuit.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2006-266587
  • Patent Document 2 Japanese Patent Application Laid-Open No. 2000-274789
  • Patent Document 1 includes a heat pump refrigerant circuit and a hot water heating circuit, and is configured to exchange heat between the refrigerant of the heat pump refrigerant circuit and the hot water of the hot water heating circuit using a water refrigerant heat exchanger. Describes a heat pump type heating device that controls the circulation pump so that the COP (heating capacity / input) is the highest for each tatami number.
  • the number of revolutions of the compressor is controlled so that the heating load on the indoor side is detected based on the difference between the indoor temperature setting value and the indoor temperature, and the heating capacity according to the indoor heating load can be exhibited. Then, in the processing procedure of the pump rotation speed control, first, the circulating pump is operated at an initial rotation speed, and the total electric input at that time is detected. Next, the rotational speed of the circulation pump is lowered, and after a certain period of operation until the operation is stabilized, the total electric input is detected again. When the total electric input has decreased from the previous time, the number of revolutions of the circulation pump is further decreased, and the process is repeated while the total electric input is decreasing. On the other hand, when the total electric input increases from the previous time, the previous pump rotation speed is the minimum value of the total electric input, and the state is restored.
  • An object of the present invention is to obtain a heat pump device that can ensure high energy efficiency even if the lengths of secondary refrigerant connection pipes are different.
  • a first aspect of the present invention for achieving the above object includes a primary refrigerant circuit, a secondary refrigerant circuit, and a control device, wherein the primary refrigerant circuit includes a compressor that compresses the primary refrigerant, a primary refrigerant, A heat source side heat exchanger that performs heat exchange with the heat source side air, a decompression device that depressurizes the primary refrigerant, and a primary refrigerant side heat transfer tube of the intermediate heat exchanger that performs heat exchange between the primary refrigerant and the secondary refrigerant.
  • the primary refrigerant circuit includes a compressor that compresses the primary refrigerant, a primary refrigerant, A heat source side heat exchanger that performs heat exchange with the heat source side air, a decompression device that depressurizes the primary refrigerant, and a primary refrigerant side heat transfer tube of the intermediate heat exchanger that performs heat exchange between the primary refrigerant and the secondary refrigerant.
  • the secondary refrigerant circuit is configured by connecting with a primary refrigerant pipe, and the secondary refrigerant circuit exchanges heat with a circulation pump that circulates the secondary refrigerant, a secondary refrigerant side heat transfer pipe of the intermediate heat exchanger, and the intermediate heat exchanger.
  • a use-side heat exchanger that performs heat exchange between the generated secondary refrigerant and the use-side medium, and a secondary refrigerant connected between the circulation pump, the secondary refrigerant-side heat transfer tube, and the use-side heat exchanger.
  • a connecting pipe and a secondary refrigerant pipe, and the control device is configured to connect the primary refrigerant.
  • the control device uses a flow rate target value set based on a parameter related to the length of the secondary refrigerant connection pipe The purpose is to control the flow rate of the circulation pump.
  • a more preferable specific configuration example in the first aspect of the present invention is as follows. (1) A compressor with a variable rotational speed is used as the compressor, and the control device determines a target flow rate value of the circulation pump based on a parameter related to a length of the secondary refrigerant connection pipe, The total power consumption of the circulation pump is set to be substantially minimum, and the flow rate of the circulation pump is controlled based on the set flow rate target value.
  • the second aspect of the present invention includes a primary refrigerant circuit, a secondary refrigerant circuit, and a control device, and the primary refrigerant circuit includes a variable speed compressor that compresses the primary refrigerant, a primary refrigerant, and a heat source side.
  • a primary refrigerant tube includes a heat source side heat exchanger that performs heat exchange with air, a decompression device that decompresses the refrigerant, and a primary refrigerant side heat transfer tube of an intermediate heat exchanger that performs heat exchange between the primary refrigerant and the secondary refrigerant.
  • the secondary refrigerant circuit includes a circulation pump that circulates the secondary refrigerant, a secondary refrigerant side heat transfer pipe of the intermediate heat exchanger, a first secondary refrigerant connection pipe, A usage-side heat exchanger that exchanges heat between the secondary refrigerant heat-exchanged by the intermediate heat exchanger and the usage-side medium, and a second secondary refrigerant connection pipe are sequentially connected by a secondary refrigerant pipe.
  • the control device controls devices of the primary refrigerant circuit and the secondary refrigerant circuit. In the constructed heat pump device, the control device determines the target flow rate value of the circulation pump corresponding to the rotational speed of the compressor based on a parameter related to the length of the secondary refrigerant connection pipe.
  • the total power consumption of the circulation pump is set to be substantially the minimum, and the flow rate of the circulation pump is controlled based on the set flow rate target value.
  • a more preferable specific configuration example in the first aspect or the second aspect of the present invention is as follows.
  • the compressor, the heat source side heat exchanger, the pressure reducing device, the intermediate heat exchanger and the circulation pump are installed in a heat source side unit, and the usage side heat exchanger is installed in a usage side unit,
  • coolant connection piping is comprised by the reciprocating secondary refrigerant
  • the parameter related to the length of the secondary refrigerant connection pipe is the length of the secondary refrigerant connection pipe.
  • a parameter related to the length of the secondary refrigerant connection pipe is a pump flow rate at a predetermined rotational speed of the circulation pump.
  • a parameter related to the length of the secondary refrigerant connection pipe is a pump head at a predetermined rotational speed of the circulation pump.
  • the control device includes pipe length input means that allows an installation operator to directly input the length of the secondary refrigerant connection pipe, and the secondary refrigerant connection pipe input by the pipe length input means.
  • the flow rate target value is set based on the length, and the flow rate of the circulation pump is controlled based on the set flow rate target value.
  • a primary refrigerant circuit, a secondary refrigerant circuit, and a control device are provided, and the primary refrigerant circuit heats the compressor that compresses the primary refrigerant, the primary refrigerant, and the heat source side air.
  • the heat source side heat exchanger that performs the exchange, the decompression device that decompresses the refrigerant, and the primary refrigerant side heat transfer tube of the intermediate heat exchanger that performs heat exchange between the primary refrigerant and the secondary refrigerant are connected by a primary refrigerant line.
  • the secondary refrigerant circuit uses a circulation pump that circulates the secondary refrigerant, a secondary refrigerant side heat transfer tube of the intermediate heat exchanger, and a secondary refrigerant that exchanges heat with the intermediate heat exchanger.
  • a use side heat exchanger that performs heat exchange with the side medium, and a secondary refrigerant connection pipe connected between the circulation pump, the secondary refrigerant side heat transfer tube, and the use side heat exchanger.
  • the controller is configured by connecting with a refrigerant pipe, and the control device includes the primary refrigerant circuit device and the secondary cooling circuit.
  • the control device In the heat pump device configured to control the devices of the circuit, the control device, the longer the length of the secondary refrigerant connection pipe, is to set a small flow rate target value of the circulating pump.
  • a primary refrigerant circuit compresses the primary refrigerant with variable rotation speed.
  • a heat source side heat exchanger for exchanging heat between the primary refrigerant and outdoor air, a decompression device for depressurizing the refrigerant, and an intermediate heat exchanger for exchanging heat between the primary refrigerant and the secondary refrigerant.
  • the heat source side fan is installed so as to blow outdoor air to the heat source side heat exchanger, and the secondary refrigerant circuit circulates the secondary refrigerant.
  • the use side heat exchanger and the second secondary refrigerant connection pipe The use side fan is installed so as to blow indoor air to the use side heat exchanger, and the control device includes the devices of the primary refrigerant circuit and the secondary refrigerant circuit.
  • the compressor, the heat source side heat exchanger, the pressure reducing device, the intermediate heat exchanger and the circulation pump are installed in a heat source side unit, and the use side heat exchanger is
  • the secondary refrigerant connection pipe is installed in a use side unit, and the secondary refrigerant connection pipe is constituted by a reciprocating secondary refrigerant connection pipe connecting the heat source side unit and the use side unit, and the control device includes the secondary refrigerant connection pipe
  • a pipe length input means that allows the installer to directly input the length of the pipe, and sets the flow rate target value based on the length of the secondary refrigerant connection pipe input by the pipe length input means. Set It is to control the flow rate of the circulation pump based on the amount target value.
  • a fifth aspect of the present invention includes a primary refrigerant circuit, a secondary refrigerant circuit, and a control device, wherein the primary refrigerant circuit is a compressor that compresses the primary refrigerant, heat of the primary refrigerant and the heat source side air.
  • the primary refrigerant circuit is a compressor that compresses the primary refrigerant, heat of the primary refrigerant and the heat source side air.
  • a heat source side heat exchanger that performs exchange, a pressure reducing device that depressurizes the primary refrigerant, and a primary refrigerant side heat transfer pipe of the intermediate heat exchanger that performs heat exchange between the primary refrigerant and the secondary refrigerant are connected by a primary refrigerant line.
  • the secondary refrigerant circuit includes a circulation pump that circulates the secondary refrigerant, a secondary refrigerant side heat transfer tube of the intermediate heat exchanger, a secondary refrigerant heated by the intermediate heat exchanger, and a hot water supply.
  • a use-side heat exchanger that exchanges heat with hot water stored in a tank, and a secondary refrigerant connection that is connected between the circulation pump, the secondary refrigerant-side heat transfer tube, and the use-side heat exchanger
  • a pipe connected to a secondary refrigerant pipe, and the control device is configured to connect the primary refrigerant.
  • the compressor, the heat source side heat exchanger, the pressure reducing device, the intermediate heat exchanger, and the circulation pump are on the heat source side
  • Installed in the unit, the use side heat exchanger and the hot water supply tank are installed in the use side unit
  • the secondary refrigerant connection pipe is a reciprocating secondary refrigerant connection for connecting the heat source side unit and the use side unit.
  • the control device comprises a pipe length input means that allows an installation operator to directly input the length of the secondary refrigerant connection pipe, and the secondary refrigerant connection input by the pipe length input means.
  • the flow rate target value is set based on the length of the pipe, and the flow rate of the circulation pump is controlled based on the set flow rate target value.
  • a primary refrigerant circuit, a secondary refrigerant circuit, and a control device are provided, and the primary refrigerant circuit heats the compressor that compresses the primary refrigerant, the primary refrigerant, and the heat source side air.
  • a heat source side heat exchanger that performs exchange, a pressure reducing device that depressurizes the primary refrigerant, and a primary refrigerant side heat transfer pipe of the intermediate heat exchanger that performs heat exchange between the primary refrigerant and the secondary refrigerant are connected by a primary refrigerant line.
  • the secondary refrigerant circuit includes a circulation pump that circulates the secondary refrigerant, a secondary refrigerant side heat transfer tube of the intermediate heat exchanger, and a secondary refrigerant that has exchanged heat with the intermediate heat exchanger.
  • a utilization side heat exchanger that performs heat exchange with the utilization side medium, and a secondary refrigerant connection pipe connected between the circulation pump, the secondary refrigerant side heat transfer tube, and the utilization side heat exchanger.
  • a secondary refrigerant pipe connected to each other, and the control device includes the primary refrigerant circuit device and the second refrigerant circuit.
  • the control device rotates the circulation pump according to a pump rotation speed target value set based on a parameter related to the length of the secondary refrigerant connection pipe. It is to control the speed.
  • the heat pump device of the present invention high energy efficiency can be ensured even if the length of the secondary refrigerant connection pipe is different.
  • a heat pump device 100 according to a first embodiment of the present invention will be described with reference to FIGS.
  • the heat pump device 100 of the first embodiment is an example of a heat pump type air conditioner, and in the description of the first embodiment, the heat pump device will be described as the air conditioner 100.
  • FIG. 1 is a system diagram of the air conditioner 100.
  • the air conditioner 100 includes an outdoor unit 1 that constitutes a heat source side unit and is disposed on the outdoor side, a use side unit 2 that is disposed on the indoor side, and secondary refrigerant connection pipes 21 (21a and 21b).
  • the air conditioning apparatus 100 includes a primary refrigerant circuit 3, a secondary refrigerant circuit 4, a heat source side fan 16, a use side fan 34, and a control device 51.
  • the primary refrigerant circuit 3 includes a compressor 11 that compresses the primary refrigerant into a high-temperature refrigerant, a four-way valve 12 that is an example of a switching valve that switches the flow direction of the primary refrigerant between heating operation and cooling operation, and a heat source side fan. 16, a heat source side heat exchanger 13 that performs heat exchange between the outdoor air that is a heat source side medium sent by 16 and the primary refrigerant, an expansion valve 14 that is an example of a decompression device that depressurizes the primary refrigerant, and a secondary refrigerant circuit.
  • the primary refrigerant circuit 3 is installed in the outdoor unit 1.
  • the primary refrigerant for example, natural refrigerant R290 (propane) or new refrigerant HFO1234yf, which is flammable but has an extremely low global warming potential, is used.
  • This combustible primary refrigerant is enclosed in the primary refrigerant circuit 3 installed in the outdoor unit 1 and is not enclosed in the secondary refrigerant circuit 4 arranged also in the use side unit 2. This ensures safety on the indoor side.
  • the capacity of the compressor 11 can be controlled by inverter control, and the rotation speed is variable from low speed to high speed.
  • the intermediate heat exchanger 15 includes a primary refrigerant side heat transfer tube 15a and a secondary refrigerant side heat transfer tube 15b.
  • the flow of the primary refrigerant and the secondary refrigerant is opposed to each other during the heating operation, and the flow of the primary refrigerant and the secondary refrigerant is a parallel flow during the cooling operation. Yes.
  • the secondary refrigerant circuit 4 includes an intermediate heat exchanger 15, an outdoor secondary refrigerant outgoing pipe 25, an outdoor secondary refrigerant outgoing connection port 22a, a secondary refrigerant outgoing connection pipe 21a, and an indoor secondary refrigerant outgoing connection port 23a.
  • a use-side heat exchanger 33 that is a use-side heat exchanger that performs heat exchange between the indoor air that is the use-side medium sent by the use-side fan 34 and the indoor refrigerant and the secondary refrigerant.
  • the outdoor secondary refrigerant return pipe 24 including the flow sensor 32 is connected in an annular shape.
  • the secondary refrigerant forward connection pipe 21 a and the secondary refrigerant return connection pipe 21 b constitute a reciprocating secondary refrigerant connection pipe that connects the outdoor unit 1 and the use side unit 2.
  • a nonflammable refrigerant such as water or brine is used, and is enclosed in a secondary refrigerant circuit 4 installed across the outdoor unit 1 and the use side unit 2.
  • a secondary refrigerant circuit 4 installed across the outdoor unit 1 and the use side unit 2.
  • the secondary refrigerant tank 35 adjusts the volume change due to the temperature change of the secondary refrigerant.
  • the circulation pump 31 is a pump that circulates the secondary refrigerant in the secondary refrigerant circuit 4.
  • the capacity of the circulation pump 31 can be controlled by inverter control, and the rotation speed is variable from low speed to high speed.
  • the flow sensor 32 detects the circulation flow rate of the secondary refrigerant.
  • the lengths of the secondary refrigerant connection pipes 21a and 21b are different for each individual depending on the positional relationship between the outdoor unit 1 and the use side unit 2 in the house where the air conditioner 100 is installed.
  • the air conditioner 100 includes a compressor discharge temperature sensor 41 provided in a refrigerant pipe on the outlet side of the compressor 11, an outdoor temperature sensor 42 provided on the air inlet side of the heat source side heat exchanger 13, and two outdoor units.
  • a flow rate sensor 32 provided in the secondary refrigerant circuit 4.
  • a temperature or flow rate signal detected by these sensors is input to the control device 51.
  • the control device 51 controls the compressor 11, the expansion valve 14, the circulation pump 31, and the like based on these input signals.
  • FIG. 1 the flow directions of the primary refrigerant and the secondary refrigerant during the heating operation are indicated by solid arrows, and the flow directions of the primary refrigerant and the secondary refrigerant during the cooling operation are indicated by dashed arrows.
  • the gas refrigerant compressed to high temperature and high pressure by the compressor 11 passes through the four-way valve 12 and flows into the primary refrigerant side heat transfer tube 15a of the intermediate heat exchanger 15.
  • the high-temperature and high-pressure gas refrigerant flowing in the primary refrigerant side heat transfer tube 15a flows in the secondary refrigerant side heat transfer tube 15b and is cooled by water having a temperature lower than that of the primary refrigerant, and is condensed and liquefied.
  • the high-pressure liquid refrigerant is decompressed by the expansion valve 14 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and is heated and evaporated by the outdoor air sent by the heat source side fan 16 in the heat source side heat exchanger 13. It becomes a low-pressure gas refrigerant.
  • This low-pressure gas refrigerant returns to the compressor 11 again through the four-way valve 12.
  • the gas refrigerant compressed to high temperature and high pressure by the compressor 11 flows into the heat source side heat exchanger 13 through the four-way valve 12.
  • the high-temperature and high-pressure gas refrigerant is cooled in the heat source side heat exchanger 13 by the heat source side heat exchanger 13 sent by the heat source side fan 16 and condensed and liquefied.
  • This high-pressure liquid refrigerant is decompressed by the expansion valve 14, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and flows into the primary refrigerant side heat transfer tube 15a of the intermediate heat exchanger 15.
  • the gas-liquid two-phase refrigerant flowing in the primary refrigerant side heat transfer tube 15a flows in the secondary refrigerant side heat transfer tube 15b and is heated and evaporated by water having a temperature higher than that of the primary refrigerant to become a low-pressure gas refrigerant.
  • This low-pressure gas refrigerant returns to the compressor 11 again through the four-way valve 12.
  • the control device 51 controls the rotational speed of the compressor 11 so that the water outlet temperature detected by the water outlet temperature sensor 43 of the intermediate heat exchanger 15 becomes a target value described later. As the rotational speed of the compressor 11 is increased, the water outlet temperature of the intermediate heat exchanger 15 increases in the heating operation, and the water outlet temperature of the intermediate heat exchanger 15 decreases in the cooling operation.
  • the target value of the water outlet temperature of the intermediate heat exchanger 15 is set, for example, in the range of 25 ° C. to 55 ° C. in the heating operation, according to the flowchart shown in FIG.
  • the basic operation of this flowchart is to change the water outlet temperature target value of the intermediate heat exchanger 15 based on the difference between the indoor set temperature set by a remote controller (not shown) and the indoor temperature. If the room temperature is within ⁇ 0.5 ° C. of the room set temperature, the water outlet temperature target value is not changed.
  • step S1 it waits for a fixed time to elapse after the heating operation is started (step S1), and when this has elapsed, the room temperature detected by the room temperature sensor 45 provided in the use side unit 2 and the remote controller are set.
  • the indoor set temperature + 0.5 ° C. is compared (step S2). In this comparison, when the room temperature is higher than the room set temperature + 0.5 ° C., a value obtained by subtracting ⁇ T from the old target value of the water outlet temperature of the use side heat exchanger 15 is set as the new target value (step S3).
  • ⁇ T at this time is obtained by multiplying the absolute value of the difference between the room temperature and the room set temperature by a coefficient k, and the target value of the water outlet temperature is lowered by an amount proportional to the difference between the room temperature and the room set temperature. It is done.
  • step S4 the new target value of the water outlet temperature is compared with the lower limit set value 25 ° C.
  • step S4 the new target value is set to the lower limit set value 25 ° C.
  • step S5 the process returns to step S1. If the new target value is not less than 25 ° C. in step S4, the process directly returns to step S1.
  • step S2 when the room temperature is equal to or lower than the room set temperature + 0.5 ° C., the room temperature detected by the room temperature sensor 45 is compared with the room set temperature ⁇ 0.5 ° C. set by the remote controller (step S6). .
  • a value obtained by adding ⁇ T to the old target value of the water outlet temperature of the intermediate heat exchanger 15 is set as the new target value (step S7).
  • ⁇ T is obtained by multiplying the absolute value of the difference between the room temperature and the room set temperature by a coefficient k in the same manner as ⁇ T described above, and is proportional to the difference between the room set temperature and the room temperature.
  • the target value of the water outlet temperature is raised.
  • step S8 the new target value of the water outlet temperature is compared with the upper limit set value 55 ° C. (step S8). If the new target value exceeds the upper limit set value 55 ° C. in this comparison, the new target value is set to 55 ° C. as the upper limit set value (step S9), and the process returns to step S1. If the new target value does not exceed the upper limit set value of 55 ° C. in step S8, the process directly returns to step S1.
  • step S6 when the room temperature is equal to or higher than the room set temperature ⁇ 0.5 ° C., that is, when step S2 and step S6 are combined and the room temperature is within ⁇ 0.5 ° C. of the set temperature, intermediate heat exchange is performed. Return to step S1 without changing the water outlet temperature target value of the vessel 15.
  • the target value of the water outlet temperature of the intermediate heat exchanger 15 is set so that the indoor temperature becomes the indoor set temperature, and the water outlet temperature detected by the water outlet temperature sensor 43 becomes this target value.
  • the rotational speed control of the compressor 11 is performed.
  • FIG. 2 shows a flowchart of the heating operation.
  • a target value of the water outlet temperature is set in a range of, for example, 7 ° C. to 20 ° C., and the water outlet temperature detected by the water outlet temperature sensor 43 is The rotation speed of the compressor 11 is controlled so as to reach this target value.
  • control device 51 controls the opening degree of the expansion valve 14 so that the discharge temperature detected by the compressor discharge temperature sensor 41 becomes a predetermined target value.
  • FIG. 3 shows the relationship between the pump flow rate of the secondary refrigerant circuit 4 and the power consumption of the air conditioner 100 during rated heating capacity operation.
  • the length of the secondary refrigerant connection pipe 21 (21a, 21b) itself is a parameter (L1 (short), L2 (long)), and the parameter L1 (short) is the secondary refrigerant connection pipe 21a.
  • 21b is short
  • the parameter L2 (long) is when the total length of the secondary refrigerant connection pipes 21a, 21b is long.
  • the pump flow rate at which the power consumption of the air conditioning apparatus 100 is minimized differs depending on the length of the secondary refrigerant connection pipe 21. The reason for this will be described below.
  • the power consumption of the air conditioner 100 is composed of the power consumption of the primary refrigerant circuit 3 and the power consumption of the secondary refrigerant circuit 4.
  • the power consumption of the primary refrigerant circuit 3 is the sum of the power consumption of the compressor 11 and the power consumption of the heat source side fan 16
  • the power consumption of the secondary refrigerant circuit 4 is the power consumption of the circulation pump 31 and the consumption of the use side fan 34. It is the sum of electricity. If the rotational speeds of the heat source side fan 16 and the use side fan 34 are constant, the power consumption of the heat source side fan 16 and the use side fan 34 is constant regardless of the pump flow rate.
  • the change in the power consumption of the primary refrigerant circuit 3 with respect to the pump flow rate is due to the change in the power consumption of the compressor 11.
  • the change in the power consumption of the secondary refrigerant circuit 4 is due to the change in the power consumption of the circulation pump 31.
  • the heating capacity of the use side heat exchanger 33 is represented by the product of water specific heat, water density, water flow rate, and water inlet / outlet temperature difference. For this reason, when the pumping capacity is increased when the heating capacity is constant, the water inlet / outlet temperature difference in the use-side heat exchanger 33 is reduced, so that the target value of the water outlet temperature of the intermediate heat exchanger 15 is set low. it can. Further, by increasing the pump flow rate, the heat transfer performance of the secondary refrigerant side heat transfer tube 15b of the intermediate heat exchanger 15 is improved. Since these reduce the condensation temperature of the intermediate heat exchanger 15 of the secondary refrigerant circuit 3, the power consumption of the compressor 11 decreases. Therefore, when the pump flow rate is increased, the power consumption of the secondary refrigerant circuit 4 increases and the power consumption of the primary refrigerant circuit 3 decreases. Therefore, there is a pump flow rate at which the power consumption of the air conditioner 100 is minimized.
  • the reason why the pump flow rate at which the power consumption of the air conditioner 100 is minimized differs depending on the length of the secondary refrigerant connection pipe 21 will be described. As the length of the secondary refrigerant connection pipe 21 is longer, the flow path resistance of the connection pipe 21 is larger, so that the required head of the circulation pump 31 for flowing the same flow rate is increased and the power consumption is also increased. Therefore, the change in power consumption with respect to the pump flow rate is different between the pipe length L1 (short) and the pipe length L2 (long). Therefore, the pump flow rate at which the power consumption of the air conditioning apparatus 100 is minimized differs depending on the length of the secondary refrigerant connection pipe 21.
  • the pump flow rate at which the power consumption of the air conditioner 100 provided with the long length L2 of the secondary refrigerant connection pipe 21 is minimized is the power consumption of the air conditioner 100 provided with the short length L1 of the secondary refrigerant connection pipe 21. Is smaller than the pump flow rate.
  • the energy efficiency of the air conditioner 100 can be maintained high by controlling the secondary refrigerant circulation pump 31 at an optimum flow rate according to the length of the secondary refrigerant connection pipe 21.
  • the flow rate target value of the circulation pump 31 is set based on the parameter related to the length of the secondary refrigerant connection pipe 21 so that the total power consumption of the compressor 11 and the circulation pump 31 is substantially minimized.
  • FIGS. 4 is a flowchart of pump rotation speed control of the air conditioner 100 of FIG. 1
  • FIG. 5 is a diagram showing a performance curve of the circulation pump 31 and a resistance curve of the secondary refrigerant circuit 4
  • FIG. 6 is a connection pipe length L1. It is a figure which shows the relationship between the compressor rotational speed Nc at the time of (short) and L2 (long), and pump flow rate target value Q0.
  • the rotational speed of the circulation pump 31 is set to the initial value Nps, and the pump 31 is operated at the rotational speed Nps (step S11).
  • the flow rate is detected by the flow rate sensor 32 (step S12), and the length of the secondary refrigerant connection pipe 21 is calculated (step S13). Details thereof will be described below.
  • curve C is a performance curve showing the relationship between the flow rate and the head when the rotational speed Nps of the circulation pump 31 is Nps.
  • Curve R (R1, R2) is a resistance curve showing the pressure loss of the secondary refrigerant circuit 4
  • R1 is a resistance curve when the length of the secondary refrigerant connection pipe 21 is L1
  • R2 is a secondary refrigerant connection. It is a resistance curve when the length of the pipe 21 is L2 (here, L1 ⁇ L2).
  • the intersection P (P1, P2) between the resistance curve R and the performance curve C is the operating point of the pump.
  • the pump flow rate at the operating point P1 is Q1
  • the lift is H1
  • the pump flow rate at the operating point P2 is Q2
  • the lift is H2.
  • step S12 the water flow rate sensor 32 detects the pump flow rate, and the value is set to Q2.
  • step S13 the length of the secondary refrigerant connection pipe 21 is obtained using the formula (1) in step S13, the length is calculated as L2. Therefore, the length of the secondary refrigerant connection pipe 21 of the air conditioner 100 of FIG. 1 is estimated as L2.
  • the pump flow rate target value Q0 is set based on the length L of the secondary refrigerant connection pipe 21 in steps S14 to S16.
  • the power consumption of the air conditioner 100 is also determined by the capacity of the air conditioner 100 when the length L of the secondary refrigerant connection pipe 21 is constant.
  • the pump flow rate target value Q0 is set smaller as the length of the secondary refrigerant connection pipe 21 is longer. Since the capacity of the air conditioner 100 is proportional to the compressor rotational speed Nc as described above, this minimizes power consumption in the same capacity of the air conditioner 100 as described in FIG. Therefore, it is the same as setting the pump flow rate target value Q0 smaller as the length of the secondary refrigerant connection pipe 21 is longer.
  • step S14 data on the rotational speed Nc of the compressor 11 is received.
  • step S15 the following equation (2) of the function g representing the relationship between the compressor rotational speed Nc and the pump flow rate target value Q0 when the connection pipe length L is shown in FIG. Set the flow rate target value Q0.
  • step S16 the control device 51 controls the rotational speed of the circulation pump 31 so that the water flow rate detected by the water flow rate sensor 32 becomes the target value Q0. Then, after a lapse of a certain time (step S16), the process returns to step S14 again, and this is repeated thereafter.
  • the circulation pump 31 of the secondary refrigerant is controlled at an optimum pump flow rate, and the longer the length of the secondary refrigerant connection pipe 21, the longer the pump of the circulation pump 31. Since the flow rate target value is set small, the energy efficiency of the air conditioner 100 can be maintained high.
  • the pump flow rate target value is set based on the connection pipe length, but any parameter can be used as long as it is a parameter related to the connection pipe length.
  • the pump flow rate at a predetermined rotational speed of the circulation pump 31 The pump head at a predetermined rotational speed of the circulation pump 31 may be used.
  • the pump flow rate target value is set based on the connection pipe length and the rotation speed of the compressor 11 related to the capacity of the air conditioner. You may set by adding the related outdoor temperature, room temperature, etc.
  • FIG. 7 is a system diagram of the air conditioner 100 according to the second embodiment of the present invention
  • FIG. 8 is a flowchart of pump rotation speed control of the air conditioner 100 of FIG.
  • the second embodiment is different from the first embodiment in the points described below, and the other points are basically the same as those in the first embodiment, and thus redundant description is omitted.
  • the air conditioner 100 of the second embodiment includes a pipe length input means 51a for directly inputting the length of the secondary refrigerant connection pipe 21 to the control device 51.
  • the installation installer inputs the length of the secondary refrigerant connection pipe 21 to the pipe length input means 51a after the installation of the air conditioner 100 is completed.
  • the control device 51 receives the data of the connection pipe length L input to the secondary refrigerant connection pipe length input means 51 (step S21). Thereafter, similarly to the first embodiment, data on the rotational speed Nc of the compressor 11 is received (step S14). Next, the pump flow rate target value Q0 is set from the connection pipe length L and the compressor rotational speed Nc (step S15). At this time, the control device 51 controls the rotational speed of the circulation pump 31 so that the water flow rate detected by the water flow rate sensor 32 becomes the target value Q0. Then, after a lapse of a predetermined time (step S16), the process returns to step S14 again, and this is repeated thereafter.
  • the air conditioner can be easily controlled by controlling the circulation pump 31 of the secondary refrigerant at an optimum pump flow rate according to the length of the secondary refrigerant connection pipe input by the installer.
  • the energy efficiency of 100 can be kept high.
  • the secondary refrigerant circulation pump 31 can be controlled with higher accuracy.
  • the pump flow rate target value Q0 is given, but instead, a pump rotation speed target value that becomes the pump flow rate target value Q0 may be given.
  • the flow sensor 32 of water can be made unnecessary and cost reduction can be aimed at.
  • FIG. 9 is a system diagram of a hot water supply apparatus according to the third embodiment of the present invention.
  • the third embodiment is different from the second embodiment in the following points, and the other points are basically the same as those in the second embodiment, and thus redundant description is omitted.
  • the heat pump device 100 of the third embodiment is an example of a heat pump type hot water supply device, and in the description of the third embodiment, the heat pump device will be described as the hot water supply device 100.
  • the primary refrigerant circuit 3 of the hot water supply device 100 does not include the four-way valve 12, and the primary refrigerant side heat transfer pipe 15 a of the compressor 11, the heat source side heat exchanger 13, the expansion valve 14, and the intermediate heat exchanger 15 is primary in an annular shape. It is configured by connecting with a refrigerant pipe. Accordingly, the primary refrigerant flows in one direction in the primary refrigerant circuit 3 as indicated by the solid line arrow.
  • the use side unit 2 is installed not only on the indoor side but also on the outdoor side and other appropriate places, and incorporates a hot water supply tank 60.
  • the hot water supply tank 60 stores hot water supply water that is a use-side medium. This hot water supply water is supplied to a bath, kitchen, washroom, etc. through a hot water supply pipe 61.
  • the use side heat exchanger 33 of the secondary refrigerant circuit 4 is installed in the hot water supply tank 60 so as to exchange heat with hot water for the hot water supply tank 60.
  • the use-side medium is changed to hot water supply water, but the control method of the hot water supply device 100 is basically the same as the control during the heating operation of the second embodiment. Therefore, the third embodiment can achieve the same effects as those of the second embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un dispositif de pompe à chaleur permettant d'assurer un rendement énergétique élevé même lorsque des conduites de raccordement de fluide de refroidissement secondaire présentent des longueurs différentes. Le dispositif de pompe à chaleur (100) comprend : un circuit de fluide de refroidissement primaire (3) ; un circuit de fluide de refroidissement secondaire (4) ; et un dispositif de commande (51). Le dispositif de pompe à chaleur (100) comprend en outre un échangeur de chaleur intermédiaire (15) comprenant un premier tube de transfert de chaleur de fluide de refroidissement primaire (15a) à travers lequel un fluide de refroidissement primaire s'écoule et un tube de transfert de chaleur de fluide de refroidissement secondaire (15b) à travers lequel un fluide de refroidissement secondaire s'écoule, de sorte que l'échange de chaleur soit réalisé entre le fluide de refroidissement primaire et le fluide de refroidissement secondaire. Le circuit de fluide de refroidissement primaire (4) est constitué : d'une pompe de circulation (31) ; du tuyau de transfert de chaleur de fluide de refroidissement secondaire (15b) ; d'un échangeur de chaleur latéral (33) ; et d'un tuyau de raccordement de fluide de refroidissement secondaire (21). Le dispositif de commande (51) commande le débit de la pompe de circulation (31) en fonction d'un débit cible déterminé conformément à un paramètre relatif à la longueur du second tuyau de raccordement de fluide de refroidissement secondaire (21).
PCT/JP2009/006682 2008-12-17 2009-12-08 Dispositif de pompe à chaleur WO2010070842A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-320704 2008-12-17
JP2008320704A JP5150472B2 (ja) 2008-12-17 2008-12-17 ヒートポンプ装置

Publications (1)

Publication Number Publication Date
WO2010070842A1 true WO2010070842A1 (fr) 2010-06-24

Family

ID=42268524

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/006682 WO2010070842A1 (fr) 2008-12-17 2009-12-08 Dispositif de pompe à chaleur

Country Status (2)

Country Link
JP (1) JP5150472B2 (fr)
WO (1) WO2010070842A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103998870A (zh) * 2012-01-18 2014-08-20 三菱电机株式会社 空气调节装置
CN106352507A (zh) * 2016-11-07 2017-01-25 珠海格力电器股份有限公司 一种水循环系统及其水流开关断流值调节方法和装置
WO2019008742A1 (fr) * 2017-07-07 2019-01-10 三菱電機株式会社 Dispositif à cycle frigorifique
EP3306216A4 (fr) * 2015-06-04 2019-02-20 Mitsubishi Electric Corporation Dispositif de régulation pour système à pompe à chaleur, et système à pompe à chaleur muni dudit dispositif
EP3531035A4 (fr) * 2016-10-24 2019-10-30 Mitsubishi Electric Corporation Système de climatiseur, dispositif de commande de climatiseur, procédé de climatiseur, et programme
EP3719416A1 (fr) * 2019-04-01 2020-10-07 Vaillant GmbH Pompe à chaleur avec fluide de travail inflammable
US20210310677A1 (en) * 2018-03-23 2021-10-07 Mitsubishi Electric Corporation Air-conditioning apparatus

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5677198B2 (ja) * 2011-05-27 2015-02-25 三菱電機株式会社 空冷ヒートポンプチラー
FR2979419B1 (fr) * 2011-08-30 2018-03-30 Arkema France Fluides de transfert de chaleur supercritiques a base de tetrafluoropropene
JP2014163594A (ja) * 2013-02-26 2014-09-08 Mitsubishi Electric Corp 流量制御装置及び流体回路システム
WO2015132951A1 (fr) * 2014-03-07 2015-09-11 三菱電機株式会社 Dispositif de réfrigération
JP6363428B2 (ja) * 2014-08-20 2018-07-25 株式会社Ｎｔｔファシリティーズ 熱媒体循環システム
WO2016190232A1 (fr) 2015-05-22 2016-12-01 ダイキン工業株式会社 Dispositif d'alimentation en fluide pour le réglage de la température

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03211374A (ja) * 1990-01-12 1991-09-17 Matsushita Electric Ind Co Ltd 冷暖房給湯機およびその制御方法
JPH04126945A (ja) * 1990-09-17 1992-04-27 Matsushita Refrig Co Ltd 多室冷暖房装置
JPH08200905A (ja) * 1995-01-20 1996-08-09 Hitachi Ltd 冷媒量の指示装置
JP2004293999A (ja) * 2003-03-28 2004-10-21 Hitachi Ltd 空気調和装置
JP2006003079A (ja) * 2005-08-08 2006-01-05 Mitsubishi Electric Corp 冷凍空調装置および冷凍空調装置の制御方法
JP2008025962A (ja) * 2006-07-25 2008-02-07 Matsushita Electric Ind Co Ltd ヒートポンプ給湯装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03211374A (ja) * 1990-01-12 1991-09-17 Matsushita Electric Ind Co Ltd 冷暖房給湯機およびその制御方法
JPH04126945A (ja) * 1990-09-17 1992-04-27 Matsushita Refrig Co Ltd 多室冷暖房装置
JPH08200905A (ja) * 1995-01-20 1996-08-09 Hitachi Ltd 冷媒量の指示装置
JP2004293999A (ja) * 2003-03-28 2004-10-21 Hitachi Ltd 空気調和装置
JP2006003079A (ja) * 2005-08-08 2006-01-05 Mitsubishi Electric Corp 冷凍空調装置および冷凍空調装置の制御方法
JP2008025962A (ja) * 2006-07-25 2008-02-07 Matsushita Electric Ind Co Ltd ヒートポンプ給湯装置

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103998870A (zh) * 2012-01-18 2014-08-20 三菱电机株式会社 空气调节装置
EP2806228A4 (fr) * 2012-01-18 2015-10-14 Mitsubishi Electric Corp Climatiseur
CN103998870B (zh) * 2012-01-18 2016-09-14 三菱电机株式会社 空气调节装置
EP3306216A4 (fr) * 2015-06-04 2019-02-20 Mitsubishi Electric Corporation Dispositif de régulation pour système à pompe à chaleur, et système à pompe à chaleur muni dudit dispositif
EP3531035A4 (fr) * 2016-10-24 2019-10-30 Mitsubishi Electric Corporation Système de climatiseur, dispositif de commande de climatiseur, procédé de climatiseur, et programme
US11300302B2 (en) 2016-10-24 2022-04-12 Mitsubishi Electric Corporation Air conditioner system, air conditioner control device, air conditioner method, and program for control using water circulation and based on indoor latent and sensible heat loads
CN106352507A (zh) * 2016-11-07 2017-01-25 珠海格力电器股份有限公司 一种水循环系统及其水流开关断流值调节方法和装置
CN106352507B (zh) * 2016-11-07 2019-01-18 珠海格力电器股份有限公司 一种水循环系统及其水流开关断流值调节方法和装置
WO2019008742A1 (fr) * 2017-07-07 2019-01-10 三菱電機株式会社 Dispositif à cycle frigorifique
JPWO2019008742A1 (ja) * 2017-07-07 2020-05-21 三菱電機株式会社 冷凍サイクル装置
US20210310677A1 (en) * 2018-03-23 2021-10-07 Mitsubishi Electric Corporation Air-conditioning apparatus
EP3719416A1 (fr) * 2019-04-01 2020-10-07 Vaillant GmbH Pompe à chaleur avec fluide de travail inflammable

Also Published As

Publication number Publication date
JP5150472B2 (ja) 2013-02-20
JP2010144963A (ja) 2010-07-01

Similar Documents

Publication Publication Date Title
JP5150472B2 (ja) ヒートポンプ装置
JP5642207B2 (ja) 冷凍サイクル装置及び冷凍サイクル制御方法
JP5642203B2 (ja) ヒートポンプ装置及びヒートポンプ装置の制御方法
JP5745651B2 (ja) 空気調和装置
JP5182358B2 (ja) 冷凍装置
JP2011257126A (ja) 空気調和装置の運転制御装置及びそれを備えた空気調和装置
WO2017203655A1 (fr) Dispositif de climatisation et d'alimentation en eau chaude de type pompe à chaleur
AU2012392672B2 (en) Air conditioning apparatus
JP4840522B2 (ja) 冷凍装置
WO2016194098A1 (fr) Dispositif de climatisation et dispositif de commande de fonctionnement
JP2005249384A (ja) 冷凍サイクル装置
WO2012050087A1 (fr) Appareil de source de chaleur
JPWO2018116410A1 (ja) 空気調和装置
WO2015115251A1 (fr) Dispositif de climatisation
JP6616925B2 (ja) ヒートポンプ装置
EP2808622A1 (fr) Dispositif de climatisation
WO2014122735A1 (fr) Dispositif de réfrigération
EP2808625A1 (fr) Procédé de remplissage en réfrigérant destiné à une unité de climatisation et unité de climatisation
US20190376702A1 (en) Method for sequencing compressor operation based on space humidity
JP6603627B2 (ja) 空調システム及び運転制御方法
EP2339267B1 (fr) Appareil à cycle de réfrigération, climatiseur d'air alimenté en eau chaude de type pompe à chaleur et unité d'extérieur correspondante
JP7086276B2 (ja) 空気調和装置
JP2012215353A (ja) 二元冷凍サイクル装置
JP6561551B2 (ja) 冷凍装置
JP2013181730A (ja) ヒートポンプ式給湯装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09833152

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 09833152

Country of ref document: EP

Kind code of ref document: A1