WO2021095124A1 - Refrigeration cycle device - Google Patents

Refrigeration cycle device Download PDF

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Publication number
WO2021095124A1
WO2021095124A1 PCT/JP2019/044375 JP2019044375W WO2021095124A1 WO 2021095124 A1 WO2021095124 A1 WO 2021095124A1 JP 2019044375 W JP2019044375 W JP 2019044375W WO 2021095124 A1 WO2021095124 A1 WO 2021095124A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
source side
heat source
refrigerant
side heat
Prior art date
Application number
PCT/JP2019/044375
Other languages
French (fr)
Japanese (ja)
Inventor
拓也 松田
周平 水谷
央貴 丸山
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2021555660A priority Critical patent/JP7183447B2/en
Priority to PCT/JP2019/044375 priority patent/WO2021095124A1/en
Priority to US17/641,551 priority patent/US20220299247A1/en
Publication of WO2021095124A1 publication Critical patent/WO2021095124A1/en

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    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • 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
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor 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
    • F25B2313/027—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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/01—Timing
    • 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
    • F25B2600/2519—On-off valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator

Definitions

  • the present invention relates to a refrigeration cycle device that harmonizes the air in the air-conditioned space.
  • the heat exchanger disclosed in Patent Document 1 has a main heat exchange unit and a sub heat exchange unit provided at different positions in the vertical direction from the main heat exchange unit and connected in series with the main heat exchange unit.
  • the main heat exchange section is provided with more flat tubes than the sub heat exchange section located on the downstream side of the main heat exchange section. Further, a flat tube at the bottom of the heat exchanger is provided in the main heat exchanger on the upstream side of the sub heat exchanger.
  • the refrigerant discharged from the compressor during the defrosting operation flows into the sub heat exchange section after passing through the main heat exchange section. That is, the refrigerant discharged from the compressor flows through the main heat exchange section even after the defrosting of the main heat exchange section is completed and before it flows into the sub heat exchange section. Therefore, the heat of the refrigerant is wasted because the refrigerant and the air are heat-exchanged in the main heat exchange section that does not require defrosting before reaching the sub heat exchange section. As a result, defrosting cannot be performed efficiently.
  • the present invention has been made to solve the above problems, and provides a refrigeration cycle apparatus capable of efficiently defrosting.
  • the refrigeration cycle apparatus includes a compressor that compresses and discharges a refrigerant, an expansion valve that depressurizes and expands the refrigerant, a load side heat exchanger connected to the expansion valve, the compressor, and the like.
  • a flow path switching device connected to the load side heat exchanger, and a first heat source side heat exchanger and a second heat source side heat exchanger connected in parallel between the flow path switching device and the expansion valve.
  • the heat source side heat exchanger including the refrigerant, the on-off valve provided on the downstream side of the second heat source side heat exchanger of the refrigerant flowing during the defrosting operation, and the on-off valve provided on the downstream side of the second heat source side heat exchanger are discharged from the compressor during the defrosting operation.
  • It has a control device that controls the flow path switching device so that the refrigerant flows into the heat source side heat exchanger, and the control device opens the on-off valve when the defrosting operation is started.
  • the on-off valve is changed from the closed state to the open state according to the first defrosting means for switching from the open state to the closed state, the determining means for determining the switching timing of the defrosting target, and the timing determined by the determining means.
  • It has a second defrosting means for switching.
  • the refrigerant discharged from the compressor is transferred to the first heat source side heat exchanger of the two heat source side heat exchangers. It flows intensively. After that, when the second defrosting means opens the on-off valve, most of the heat of the refrigerant is spent on defrosting the second heat source side heat exchanger. Therefore, wasteful consumption of the heat of the refrigerant is suppressed as compared with the case where two heat source side heat exchangers connected in series are defrosted at the same time. As a result, the two heat source side heat exchangers can be efficiently defrosted.
  • FIG. It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus which concerns on Embodiment 1.
  • FIG. It is a functional block diagram which shows one configuration example of the control device shown in FIG.
  • FIG. It is a hardware configuration diagram which shows one configuration example of the control device shown in FIG.
  • FIG. It is a hardware configuration diagram which shows another configuration example of the control device shown in FIG.
  • It is a flowchart which shows an example of the operation procedure of the refrigeration cycle apparatus shown in FIG.
  • FIG. It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of modification 1.
  • FIG. It is a functional block diagram which shows one configuration example of the control device in modification 1.
  • FIG. It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of the modification 2.
  • FIG. 2 It is a functional block diagram which shows one configuration example of the control device in the modification 2. It is a flowchart which shows an example of the operation procedure of the refrigeration cycle apparatus shown in FIG. It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of the modification 3. It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus which concerns on Embodiment 2.
  • FIG. It is a side view which shows one configuration example of the 1st heat source side heat exchanger shown in FIG. It is a side view which shows one configuration example of the 2nd heat source side heat exchanger shown in FIG. It is a refrigerant circuit diagram which shows the structural example of the refrigeration cycle apparatus of the comparative example.
  • FIG. 8 is an external perspective view of the heat source side unit shown in FIG. 18 when viewed from a direction different from that in the case of FIG.
  • FIG. 18 is a schematic diagram which shows the layout of the heat source side heat exchanger when the heat source side unit shown in FIG.
  • FIG. 20 is seen from the top. It is a side view which shows one configuration example of the 1st division heat exchanger shown in FIG. It is a side view which shows one configuration example of the 2nd heat source side heat exchanger shown in FIG. It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of the modification 4.
  • FIG. 1 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device according to the first embodiment.
  • the refrigeration cycle device 1 includes a heat source side unit 10, load side units 20a and 20b, and a control device 30 for controlling the heat source side unit 10 and the refrigerant equipment included in the load side units 20a and 20b.
  • FIG. 1 shows a case where the refrigeration cycle device 1 has two load-side units 20a and 20b, but the load-side unit may be one or three or more. Good.
  • the heat source side unit 10 includes a compressor 2 that compresses and discharges the refrigerant, a heat source side heat exchanger 15 that exchanges heat with the outside air, a flow path switching device 5, an accumulator 6, and an on-off valve 7. .
  • the heat source side heat exchanger 15 includes a first heat source side heat exchanger 3 and a second heat source side heat exchanger 4.
  • the load-side unit 20a includes a load-side heat exchanger 21a that exchanges heat with the air in the room where the load-side unit 20a is installed, and an expansion valve 22a that depressurizes and expands the refrigerant.
  • the load-side unit 20b includes a load-side heat exchanger 21b that exchanges heat with the air in the room where the load-side unit 20b is installed, and an expansion valve 22b that depressurizes and expands the refrigerant.
  • the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 are connected in parallel between the flow path switching device 5 and the expansion valves 22a and 22b.
  • one refrigerant inlet / outlet is connected to the first gas pipe 43a, and the other refrigerant inlet / outlet is connected to the first liquid pipe 44a.
  • one refrigerant inlet / outlet is connected to the second gas pipe 43b, and the other refrigerant inlet / outlet is connected to the second liquid pipe 44b.
  • the first gas pipe 43a and the second gas pipe 43b join the gas pipe 41 and are connected to the flow path switching device 5.
  • the first liquid pipe 44a and the second liquid pipe 44b join the liquid pipe 47 and are connected to the expansion valves 22a and 22b.
  • the on-off valve 7 is provided in the second liquid pipe 44b.
  • the flow path switching device 5 is connected to the load side heat exchangers 21a and 21b via the refrigerant pipe 42, and is connected to the accumulator 6 via the refrigerant pipe 48. Further, the flow path switching device 5 is connected to the compressor 2 and the accumulator 6 via the refrigerant pipe 49. The accumulator 6 is connected to the refrigerant suction port of the compressor 2.
  • the compressor 2, the first heat source side heat exchanger 3, the second heat source side heat exchanger 4, the expansion valve 22a, and the load side heat exchanger 21a are connected by a pipe such as a refrigerant pipe 42, and the refrigerant circuit 60a Is configured.
  • the compressor 2, the first heat source side heat exchanger 3, the second heat source side heat exchanger 4, the expansion valve 22b, and the load side heat exchanger 21b are connected by a pipe such as a refrigerant pipe 42, and the refrigerant is used.
  • the circuit 60b is configured.
  • the second heat source side heat exchanger 4 is provided with a heat exchanger temperature sensor 11 that detects the temperature Te of the refrigerant.
  • the second liquid pipe 44b is provided with a refrigerant temperature sensor 12 that detects the temperature Tn2 of the refrigerant flowing through the second liquid pipe 44b.
  • the load-side unit 20a is provided with a room temperature sensor 23a that detects the temperature of the air in the room in which the load-side unit 20a is installed.
  • the load-side unit 20b is provided with a room temperature sensor 23b that detects the temperature of the air in the room in which the load-side unit 20b is installed.
  • the heat exchanger temperature sensor 11, the refrigerant temperature sensor 12, and the room temperature sensors 23a and 23b are, for example, thermistors.
  • the heat exchanger temperature sensor 11 may be provided on the first heat source side heat exchanger 3 side instead of the second heat source side heat exchanger 4.
  • the compressor 2 is a compressor whose capacity can be changed, for example, an inverter compressor.
  • the accumulator 6 is a container that prevents the liquid refrigerant from being sucked into the compressor 2.
  • the expansion valves 22a and 22b are, for example, electronic expansion valves.
  • the flow path switching device 5 switches the flow direction of the refrigerant discharged from the compressor 2 to the gas pipe 41 or the refrigerant pipe 42.
  • the flow path switching device 5 is, for example, a four-way valve.
  • the on-off valve 7 is, for example, a shutoff valve capable of switching from one of the closed state and the open state to the other state.
  • the on-off valve 7 may be an electronic expansion valve that adjusts the flow rate of the flowing refrigerant.
  • the first heat source side heat exchanger 3, the second heat source side heat exchanger 4, and the load side heat exchangers 21a and 21b are, for example, fin-and-tube heat exchangers.
  • the control device 30 is connected to each device of the compressor 2, the flow path switching device 5, the expansion valves 22a and 22b, and the on-off valve 7 via a signal line (not shown in the figure). Further, the control device 30 is connected to each of the room temperature sensors 23a and 23b, the heat exchanger temperature sensor 11, and the refrigerant temperature sensor 12 via signal lines (not shown in the figure).
  • the communication connection between the control device 30 and each device of the compressor 2, the flow path switching device 5, the expansion valve 22a, the expansion valve 22b, and the on-off valve 7 is not limited to the wired connection, but may be wireless.
  • the communication connection between the control device 30 and each of the room temperature sensor 23a, the room temperature sensor 23b, the heat exchanger temperature sensor 11 and the refrigerant temperature sensor 12 is not limited to wired, but may be wireless.
  • the refrigerant flowing into the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 condenses by exchanging heat with air in these heat exchangers connected in parallel, and becomes a low-temperature and high-pressure liquid refrigerant. Then, it flows out from the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4.
  • the liquid refrigerant flows into the load side heat exchanger 21a.
  • the refrigerant that has flowed into the load-side heat exchanger 21a evaporates by exchanging heat with air in the load-side heat exchanger 21a, becomes a low-temperature low-pressure gas refrigerant, and flows out of the load-side heat exchanger 21a.
  • the air in the room is cooled by the refrigerant absorbing heat from the air in the room.
  • the refrigerant flowing out of the load-side heat exchanger 21a is sucked into the compressor 2 via the flow path switching device 5.
  • the cooling operation after the refrigerant discharged from the compressor 2 circulates in order through the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4, the expansion valve 22a, and the load side heat exchanger 21a. , The cycle until it is sucked into the compressor 2 is repeated.
  • the control device 30 switches the flow path of the flow path switching device 5 so that the refrigerant discharged from the compressor 2 flows into the load side heat exchanger 21a.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 2
  • the high-temperature and high-pressure gas refrigerant is discharged from the compressor 2.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the load-side heat exchanger 21a via the flow path switching device 5.
  • the refrigerant flowing into the load-side heat exchanger 21a is condensed by exchanging heat with air in the load-side heat exchanger 21a, becomes a high-temperature and high-pressure liquid refrigerant, and flows out from the load-side heat exchanger 21a.
  • the air in the room is warmed by the refrigerant dissipating heat to the air in the room.
  • the high temperature and high pressure liquid refrigerant flowing out from the load side heat exchanger 21a becomes a low temperature and low pressure liquid refrigerant by the expansion valve 22a.
  • the liquid refrigerant flows into the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4.
  • the refrigerant evaporates by exchanging heat with air to become a low-temperature low-pressure gas refrigerant, and becomes the first heat source side heat exchanger 3 and the first heat exchanger. 2 Outflow from the heat source side heat exchanger 4.
  • the refrigerant flowing out from the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 is sucked into the compressor 2 via the flow path switching device 5.
  • the refrigerant discharged from the compressor 2 is the load side heat exchanger 21a, the expansion valve 22a, the first heat source side heat exchanger 3, and the second heat source side heat. After circulating the exchanger 4 in order, the cycle until it is sucked into the compressor 2 is repeated.
  • FIG. 2 is a functional block diagram showing a configuration example of the control device shown in FIG.
  • the control device 30 includes a refrigerating cycle control means 51, a determination means 52, a timer 53, a first defrosting means 54, and a second defrosting means 55.
  • Various functions of the control device 30 are realized by executing software by an arithmetic unit such as a microcomputer. Further, the control device 30 may be composed of hardware such as a circuit device that realizes various functions.
  • the set temperature Ts1 is input to the control device 30 by the user who uses the load side unit 20a via a remote controller (not shown).
  • the set temperature Ts2 is input to the control device 30 by the user who uses the load side unit 20b via a remote controller (not shown).
  • the installation position of the control device 30 is not limited, and the control device 30 may be provided in the heat source side unit 10 or in the load side unit 20a or 20b. May be good.
  • the refrigeration cycle control means 51 controls the flow path switching device 5 according to the operation mode of the refrigeration cycle device 1.
  • the refrigeration cycle control means 51 controls the operating frequency of the compressor 2 and the opening degrees of the expansion valves 22a and 22b based on the detected values received from the room temperature sensors 23a and 23b and the set temperatures Ts1 and Ts2. Specifically, the refrigeration cycle control means 51 sets the operating frequency of the compressor 2 and the operating frequency of the compressor 2 so that the detected value of the room temperature sensor 23a approaches the set temperature Ts1 and the detected value of the room temperature sensor 23b approaches the set temperature Ts2.
  • the opening degrees of the expansion valves 22a and 22b are controlled.
  • the refrigeration cycle control means 51 monitors the temperature Te of the refrigerant received from the heat exchanger temperature sensor 11, and whether the temperature Te of the refrigerant is equal to or less than a predetermined temperature threshold T0. Judge whether or not.
  • the temperature threshold T0 is, for example, 0 ° C.
  • the refrigerating cycle control means 51 controls the flow path switching device 5 to switch the flow path and determines the defrosting start information indicating that the defrosting operation is started. Send to 52.
  • the refrigerating cycle control means 51 controls the flow path switching device 5 to switch the flow path, and switches the operation mode from the defrosting operation to the heating operation.
  • the timer 53 measures the time and provides the measurement time information to the determination means 52.
  • the determination means 52 determines the timing of switching the defrost target based on at least one of the time elapsed from the start of defrosting and the temperature Tn2 of the refrigerant detected by the refrigerant temperature sensor 12.
  • the determination means 52 receives the defrosting start information from the refrigeration cycle control means 51, the determination means 52 transfers the defrosting start information to the first defrosting means 54 and monitors the time t1 which is the elapsed time from the defrosting start.
  • the determination means 52 determines whether or not the time t1 is equal to or greater than a predetermined time threshold value tth1.
  • the time threshold value tth1 is set to the time before the defrosting of the first heat source side heat exchanger 3 is completely completed.
  • the determination means 52 transmits switching instruction information to instruct the switching of the state of the on-off valve 7 to the second defrosting means 55.
  • the determination means 52 monitors the refrigerant temperature Tn2 received from the refrigerant temperature sensor 12 after transmitting the switching instruction information to the second defrosting means 55, and the refrigerant temperature Tn2 is equal to or higher than a predetermined temperature threshold value Tb. It is determined whether or not it is.
  • the temperature threshold Tb is, for example, 7 ° C.
  • the determination means 52 transmits the defrosting end information indicating that the defrosting is completed to the refrigerating cycle control means 51.
  • the first defrosting means 54 When the first defrosting means 54 receives the defrosting start information from the determining means 52, the first defrosting means 54 switches the on-off valve 7 from the open state to the closed state.
  • the second defrosting means 55 receives the switching instruction information from the determining means 52, the second defrosting means 55 switches the on-off valve 7 from the closed state to the open state.
  • FIG. 3 is a hardware configuration diagram showing a configuration example of the control device shown in FIG.
  • the control device 30 shown in FIG. 2 is composed of a processing circuit 31 as shown in FIG.
  • Each function of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54, and the second defrosting means 55 shown in FIG. 2 is realized by the processing circuit 31.
  • the processing circuit 31 may be, for example, a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC (Application Specific Integrated Circuit), or an FPGA (Field-Programmable Gate). It corresponds to Array) or a combination of these.
  • Each of the functions of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54 and the second defrosting means 55 may be realized by the processing circuit 31, and the function of each means may be 1 It may be realized by one processing circuit 31.
  • FIG. 4 is a hardware configuration diagram showing another configuration example of the control device shown in FIG.
  • the control device 30 shown in FIG. 2 includes a processor 71 and a memory 72 as shown in FIG.
  • the functions of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54, and the second defrosting means 55 are realized by the processor 71 and the memory 72.
  • FIG. 4 shows that the processor 71 and the memory 72 are communicably connected to each other.
  • the functions of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54 and the second defrosting means 55 are software, firmware, or software and firmware. It is realized by the combination.
  • the software and firmware are written as a program and stored in the memory 72.
  • the processor 71 realizes the function of each means by reading and executing the program stored in the memory 72.
  • a non-volatile semiconductor memory such as a ROM (Read Only Memory), a flash memory, an EPROM (Erasable and Programmable ROM) and an EPROM (Electrically Erasable and Programmable ROM) is used.
  • a volatile semiconductor memory of RAM Random Access Memory
  • a removable recording medium such as a magnetic disk, a flexible disk, an optical disk, a CD (Compact Disc), an MD (Mini Disc), or a DVD (Digital Versaille Disc) may be used.
  • FIG. 5 is a flowchart showing an example of the operation procedure of the refrigeration cycle apparatus shown in FIG.
  • FIG. 5 shows an example of an operation procedure when the refrigerating cycle device 1 performs a defrosting operation. It is assumed that the refrigerating cycle device 1 is in the heating operation before starting the operation procedure shown in FIG. 5, and the on-off valve 7 is in the open state.
  • the refrigeration cycle control means 51 determines whether or not the temperature Te of the refrigerant received from the heat exchanger temperature sensor 11 is equal to or lower than the temperature threshold value T0 (step S101). In step S101, the refrigeration cycle control means 51 determines that frost has adhered to the heat source side heat exchanger 15 when the temperature Te of the refrigerant becomes equal to or lower than the temperature threshold value T0, and controls the flow path switching device 5 to control the flow path. Switching (step S102). As a result, the refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 15 via the flow path switching device 5. Further, the refrigeration cycle control means 51 transmits the defrosting start information to the determination means 52 in step S102.
  • the determination means 52 When the determination means 52 receives the defrosting start information from the refrigerating cycle control means 51, the determination means 52 transfers the defrosting start information to the first defrosting means 54 and monitors the time t1 measured by the timer 53. When the first defrosting means 54 receives the defrosting start information from the determining means 52, the first defrosting means 54 closes the on-off valve 7 (step S103). The determination means 52 determines whether or not the time t1 is equal to or greater than the time threshold value tth1 (step S104). In step S104, the determination means 52 transmits the switching instruction information to the second defrosting means 55 when the time t1 becomes the time threshold value tth1 or more.
  • the second defrosting means 55 receives the switching instruction information from the determining means 52, the on-off valve 7 is opened (step S105).
  • the determining means 52 determines whether or not the temperature Tn2 of the refrigerant received from the refrigerant temperature sensor 12 is equal to or higher than the temperature threshold value Tb (step S106).
  • the determination means 52 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and transmits the defrosting completion information to the refrigeration cycle control means 51.
  • the refrigeration cycle control means 51 When the refrigeration cycle control means 51 receives the defrosting end information from the determination means 52, the refrigeration cycle control means 51 controls the flow path switching device 5 to switch the flow path (step S107). As a result, the refrigerant discharged from the compressor 2 flows into the load-side units 20a and 20b via the flow path switching device 5. The operation mode of the refrigeration cycle device 1 returns from the defrosting operation to the heating operation.
  • the first heat source side heat exchanger 3 is intensively defrosted from the time when the refrigeration cycle device 1 starts defrosting until the time t1 reaches the time threshold value tth1.
  • the refrigeration cycle apparatus 1 starts defrosting the second heat source side heat exchanger 4 before the defrosting of the first heat source side heat exchanger 3 is completed, but the first heat source side heat exchanger 3 is defrosted.
  • the determination means 52 determines whether or not the defrosting of the second heat source side heat exchanger 4 is completed by the temperature Tn1 of the refrigerant on the downstream side of the second heat source side heat exchanger 4.
  • the defrosting of the first heat source side heat exchanger 3 is also completed. ..
  • the refrigerant temperature sensor 12 is provided in the second liquid pipe 44b, but the refrigerant temperature is in the liquid pipe 47 near the confluence of the first liquid pipe 44a and the second liquid pipe 44b.
  • the sensor 12 may be provided.
  • the determination means 52 determines whether or not the temperature Tn2 of the refrigerant is equal to or higher than a predetermined temperature threshold value Ta. Then, as a result of the determination in step S104, when the temperature Tn2 of the refrigerant is equal to or higher than the temperature threshold Ta, the determination means 52 may transmit the switching instruction information to the second defrosting means 55.
  • the temperature thresholds Ta and Tb have a relationship of, for example, Ta> Tb. Even if the refrigeration cycle device 1 proceeds to the process of step S105 before the defrosting of the first heat source side heat exchanger 3 is completely completed due to the relationship of Ta> Tb, the refrigerant also remains in the first heat source side heat exchanger 3. Defrosting is performed for distribution. Further, when the refrigerant temperature sensor 12 is provided in the liquid pipe 47, the timer 53 may not be provided in the control device 30.
  • the refrigeration cycle device 1 of the first embodiment includes a compressor 2, an expansion valve 22a, a load side heat exchanger 21a, a flow path switching device 5, a heat source side heat exchanger 15, an on-off valve 7, and the like. It has a control device 30 and.
  • the heat source side heat exchanger 15 has a first heat source side heat exchanger 3 and a second heat source side heat exchanger 4 connected in parallel between the flow path switching device 5 and the expansion valve 22a.
  • the on-off valve 7 is provided on the downstream side of the second heat source side heat exchanger 4 of the refrigerant that circulates during the defrosting operation.
  • the control device 30 controls the flow path switching device 5 so that the refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 15 during the defrosting operation.
  • the control device 30 includes a first defrosting means 54, a determining means 52, and a second defrosting means 55.
  • the first defrosting means 54 switches the on-off valve 7 from the open state to the closed state when the defrosting operation is started.
  • the determination means 52 determines the timing of switching the defrost target.
  • the second defrosting means switches the on-off valve 7 from the closed state to the open state according to the timing determined by the determination means 52.
  • the first defrosting means 54 closes the on-off valve 7 at the start of defrosting, so that the refrigerant discharged from the compressor 2 is the first of the two heat source side heat exchangers. It flows intensively to the heat exchanger 3 on the heat source side.
  • the second defrosting means 55 opens the on-off valve 7.
  • the refrigerant flows to the second heat source side heat exchanger 4, but also flows to the first heat source side heat exchanger 3.
  • most of the heat of the refrigerant is consumed in the second heat source side heat exchanger 4, and the frost remaining in the first heat source side heat exchanger 3 melts.
  • the first modification is the case where the refrigerating cycle device 1 shown in FIG. 1 is not provided with the refrigerant temperature sensor 12.
  • the same components as those described with reference to FIGS. 1 to 5 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • FIG. 6 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the first modification.
  • FIG. 7 is a functional block diagram showing a configuration example of the control device in the first modification.
  • the heat source side unit 10a of the refrigeration cycle device 1a is not provided with the refrigerant temperature sensor 12 shown in FIG.
  • the determining means 52 determines whether or not the time t1 measured by the timer 53 is equal to or greater than the predetermined time threshold tth2.
  • the time thresholds tth1 and tth2 have a relationship of tth1 ⁇ tth2.
  • the determination means 52 transmits the defrosting end information to the refrigeration cycle control means 51.
  • step S106 the determination means 52 determines whether or not the time t1 measured by the timer 53 is equal to or greater than the time threshold value tth2. As a result of the determination in step S106, when the time t1 becomes the time threshold value tth2 or more, the determination means 52 transmits the defrosting end information to the refrigeration cycle control means 51.
  • the effect of the first embodiment can be obtained even if the refrigerant temperature sensor 12 is not provided.
  • Modification 2 The second modification is the case where the flow rate adjusting valve and the refrigerant temperature sensor are provided in the first liquid pipe 44a in the refrigerating cycle device 1 shown in FIG.
  • the same components as those described with reference to FIGS. 1 to 7 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • FIG. 8 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the second modification.
  • FIG. 9 is a functional block diagram showing a configuration example of the control device in the second modification.
  • a refrigerant temperature sensor 12a and a flow rate adjusting valve 9 are provided in the first liquid pipe 44a of the heat source side unit 10b of the refrigeration cycle device 1b.
  • the refrigerant temperature sensor 12a detects the temperature Tn1 of the refrigerant flowing through the first liquid pipe 44a.
  • the flow rate adjusting valve 9 can switch from one of the closed state and the open state to the other state.
  • the flow rate adjusting valve 9 can adjust the flow rate of the flowing refrigerant by changing the opening degree.
  • the control device 30 of the second modification does not have the timer 53 shown in FIG.
  • the control device 30 stores in advance the temperature threshold value Ta as a value that serves as a determination standard for determining the timing of switching the defrosting target for the refrigerant temperature Tn1.
  • Ta and Tb may have the same value or different values.
  • FIG. 10 is a flowchart showing an example of the operation procedure of the refrigeration cycle apparatus shown in FIG. It is assumed that the refrigerating cycle device 1b is in the heating operation before starting the operation procedure shown in FIG. 10, and the flow rate adjusting valve 9 and the on-off valve 7 are in the open state. Since the processes of steps S201 and S202 shown in FIG. 10 are the same as the processes of steps S101 and S102 described with reference to FIG. 5, detailed description thereof will be omitted.
  • step S201 After the determination in step S201, when the determination means 52 receives the defrosting start information from the refrigeration cycle control means 51, the determination means 52 transfers the defrosting start information to the first defrosting means 54 and is detected by the refrigerant temperature sensor 12a. The temperature Tn1 of the refrigerant is monitored. When the first defrosting means 54 receives the defrosting start information from the determining means 52, the first defrosting means 54 closes the on-off valve 7 (step S203). The determination means 52 determines whether or not the temperature Tn1 of the refrigerant is equal to or higher than the temperature threshold value Ta (step S204). In step S204, when the temperature Tn1 of the refrigerant becomes equal to or higher than the temperature threshold value Ta, the determination means 52 transmits the switching instruction information to the second defrosting means 55.
  • the determining means 52 determines whether or not the temperature Tn2 of the refrigerant detected by the refrigerant temperature sensor 12b is equal to or higher than the temperature threshold value Tb (step S207). When the temperature Tn2 of the refrigerant becomes equal to or higher than the temperature threshold value Tb, the determination means 52 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and sends the defrosting end information to the second defrosting means 55 and the refrigeration cycle control means 51. Send to.
  • the second defrosting means 55 When the second defrosting means 55 receives the defrosting end information from the determination means 52, the second defrosting means 55 opens the flow rate adjusting valve 9 (step S208).
  • the refrigeration cycle control means 51 When the refrigeration cycle control means 51 receives the defrosting end information from the determination means 52, the refrigeration cycle control means 51 controls the flow path switching device 5 to switch the flow path (step S209). As a result, the refrigerant discharged from the compressor 2 flows into the load-side units 20a and 20b via the flow path switching device 5. The operation mode of the refrigeration cycle device 1 returns from the defrosting operation to the heating operation.
  • step S206 shown in FIG. 10 the second defrosting means 55 closes the flow rate adjusting valve 9, but does not completely close the flow rate adjusting valve 9 and reduces the opening degree of the flow rate adjusting valve 9.
  • the refrigerant may be circulated a little.
  • step S208 the second defrosting means 55 fully opens the flow rate adjusting valve 9.
  • a valve for shutting off the flow of the refrigerant is provided in each of the liquid pipes of the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 connected in parallel.
  • the refrigeration cycle device 1b of the second modification controls the opening and closing of each valve during the defrosting operation to first intensively defrost the first heat source side heat exchanger 3, and then the remaining second heat source side heat. By intensively defrosting the exchanger 4, defrosting can be performed reliably and efficiently.
  • the determination means 52 determines the timing at which the main defrost target is switched from the first heat source side heat exchanger 3 to the second heat source side heat exchanger 4 based on the temperature Tn1 of the refrigerant. Therefore, the determination means 52 can more accurately determine the state of whether or not frost remains in the first heat source side heat exchanger 3 than the time t1 measured by the timer 53. Further, according to the second modification, the timer 53 may not be provided in the control device 30.
  • Modification example 3 is a case where three or more heat source side heat exchangers are connected in parallel in the refrigeration cycle apparatus 1 shown in FIG.
  • the same components as those described with reference to FIGS. 1 to 10 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • FIG. 11 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the modified example 3.
  • the third heat source side heat exchanger 8 connected in parallel with the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 It is provided.
  • the third heat source side heat exchanger 8 is connected to the gas pipe 41 via the third gas pipe 43c, and is connected to the liquid pipe 47 via the third liquid pipe 44c.
  • the third liquid pipe 44c is provided with a refrigerant temperature sensor 12c and a second flow rate adjusting valve 9b.
  • the refrigerant temperature sensor 12c detects the temperature Tn3 of the refrigerant flowing through the third liquid pipe 44c.
  • the determination means 52 compares the temperature Tn3 of the refrigerant with the predetermined temperature threshold Td, and when the temperature Tn3 of the refrigerant becomes equal to or higher than the temperature threshold Td, the defrosting target is switched.
  • the first flow rate adjusting valve 9a and the second flow rate adjusting valve 9b have the same configuration as the flow rate adjusting valve 9, and the refrigerant temperature sensor 12c has the same configuration as the refrigerant temperature sensor 12. Omit.
  • the operation of the refrigeration cycle device 1c of the second modification will be described with reference to FIG.
  • a process different from the process shown in FIG. 10 will be described, and detailed description of the process similar to the process described with reference to FIG. 10 will be omitted.
  • the on-off valve 7, the first flow rate adjusting valve 9a, and the second flow rate adjusting valve 9b are in the open state.
  • step S203 when the first defrosting means 54 receives the defrosting start information from the determining means 52, the first flow rate adjusting valve 9a is maintained in the open state, and the on-off valve 7 and the second flow rate adjusting valve 9b are closed.
  • step S206 the second defrosting means 55 closes the first flow rate adjusting valve 9a.
  • step S207 when the temperature Tn2 of the refrigerant becomes equal to or higher than the temperature threshold value Tb, the determination means 52 transmits the switching instruction information to the second defrosting means 55.
  • the second defrosting means 55 receives the switching instruction information from the determining means 52, the second defrosting means 55 closes the on-off valve 7 and opens the second flow rate adjusting valve 9b.
  • the determination means 52 determines whether or not the temperature Tn3 of the refrigerant detected by the refrigerant temperature sensor 12c is equal to or higher than the temperature threshold value Td after transmitting the switching instruction information to the second defrosting means 55 based on the determination result in step S207. To do. When the temperature Tn3 of the refrigerant becomes equal to or higher than the temperature threshold value Td, the determination means 52 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and sends the defrosting end information to the second defrosting means 55 and the refrigeration cycle control means 51. Send to. After that, the control device 30 performs the processes of steps S208 and S209.
  • FIG. 11 shows a case where three heat source side heat exchangers are connected in parallel
  • the number of heat source side heat exchangers connected in parallel may be four or more.
  • a flow rate adjusting device and a refrigerant temperature sensor are provided on the liquid piping side of each heat source side heat exchanger.
  • the determination means 52 may determine the timing of switching the defrosting target based on the time t1 measured by the timer 53 shown in FIG. In this case, the refrigerant temperature sensors 12a to 12c may not be provided.
  • Embodiment 2 The refrigeration cycle apparatus of the second embodiment is a case where a header for dividing and merging the flowing refrigerant is provided in the heat source side heat exchanger.
  • the same components as those described in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted.
  • FIG. 12 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device according to the second embodiment.
  • the refrigeration cycle device 1d has a heat source side unit 10d.
  • the first gas header 61 is provided on the first gas pipe 43a side of the first heat source side heat exchanger 3, and the first liquid header 61 is provided on the first liquid pipe 44a side of the first heat source side heat exchanger 3.
  • 62 is provided.
  • the second gas header 63 is provided on the second gas pipe 43b side of the second heat source side heat exchanger 4, and the second gas header 63 is provided on the second liquid pipe 44b side of the second heat source side heat exchanger 4.
  • a liquid header 64 is provided.
  • FIG. 13 is a side view showing a configuration example of the first heat source side heat exchanger shown in FIG.
  • FIG. 14 is a side view showing a configuration example of the second heat source side heat exchanger shown in FIG.
  • the X-axis and the Z-axis are shown in the figure to define the direction.
  • the direction opposite to the Z-axis arrow shown in FIGS. 13 and 14 is the direction of gravity.
  • the solid arrows shown in FIGS. 13 and 14 indicate the flow direction of the refrigerant when the refrigerating cycle device 1 performs the cooling operation and the defrosting operation.
  • the broken line arrows shown in FIGS. 13 and 14 indicate the flow direction of the refrigerant when the refrigeration cycle device 1 performs the heating operation.
  • the first heat source side heat exchanger 3 has a plurality of heat transfer tubes 45a and a plurality of heat radiation fins 46a.
  • the first gas pipe 43a is connected to the first gas header 61.
  • the position where the first gas pipe 43a is connected to the first gas header 61 is the central portion of the height which is the length of the first gas header 61 in the direction perpendicular to the ground (Z-axis arrow direction).
  • the central portion includes not only the exact center position of the height of the first gas header 61 but also a height in a certain range with respect to the center position.
  • the first liquid pipe 44a is connected to the lower part of the first liquid header 62.
  • the first gas header 61 divides the refrigerant flowing from the first gas pipe 43a into the plurality of heat transfer pipes 45a when the refrigerating cycle device 1 performs the cooling operation and the defrosting operation.
  • the first gas header 61 merges the refrigerants flowing in from the plurality of heat transfer pipes 45a and flows out to the first gas pipe 43a.
  • the second heat source side heat exchanger 4 has a plurality of heat transfer tubes 45b and a plurality of heat radiation fins 46b.
  • the second gas pipe 43b is connected to the second gas header 63.
  • the position where the second gas pipe 43b is connected to the second gas header 63 is the central portion of the height which is the length of the second gas header 63 in the direction perpendicular to the ground (Z-axis arrow direction).
  • the central portion includes not only the exact center position of the height of the second gas header 63 but also a certain range of heights based on the center position.
  • the second liquid pipe 44b is connected to the lower part of the second liquid header 64.
  • the second gas header 63 divides the refrigerant flowing from the second gas pipe 43b into the plurality of heat transfer pipes 45b when the refrigerating cycle device 1 performs the cooling operation and the defrosting operation.
  • the second gas header 63 merges the refrigerants flowing in from the plurality of heat transfer pipes 45b and flows out to the second gas pipe 43b.
  • the height of the first heat source side heat exchanger 3 and the height of the second heat source side heat exchanger 4 are the same, and the number of heat transfer tubes 45a and the number of heat transfer tubes 45b are the same.
  • Is. 13 and 14 show the case where the number of heat transfer tubes 45a and the number of heat transfer tubes 45b is 13, but the number of heat transfer tubes 45a and 45b is not limited to 13.
  • FIG. 15 is a refrigerant circuit diagram showing a configuration example of a refrigeration cycle device of a comparative example.
  • the same components as those described with reference to FIGS. 1 and 12 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • the refrigeration cycle device 100 of the comparative example has a heat source side unit 110, load side units 20a and 20b, and a control device 130.
  • a refrigerant temperature sensor 121 is provided in the liquid pipe 47 on the downstream side of the position where the first liquid pipe 44a and the second liquid pipe 44b meet, with reference to the direction in which the refrigerant flows during the defrosting operation.
  • the refrigerant temperature sensor 121 detects the temperature Tr of the refrigerant flowing through the liquid pipe 47, and transmits information on the temperature Tr of the refrigerant to the control device 130. Since the hardware configuration of the control device 130 is the same as the configuration described with reference to FIGS. 3 and 4, detailed description thereof will be omitted.
  • the control device 130 compares the temperature Tr of the refrigerant with the predetermined temperature threshold Tc. Then, the control device 130 determines that the defrosting is completed when the temperature Tr of the refrigerant becomes equal to or higher than the temperature threshold value Tc.
  • the temperature threshold Tc is, for example, 10 ° C.
  • the temperature thresholds Tb and Tc have a relationship of Tc> Tb. Further, when the temperature threshold value Tc is compared with the temperature threshold value Ta described in the second modification, the relationship is Ta ⁇ Tc.
  • FIG. 16 is a flowchart showing an example of the operation procedure of the refrigeration cycle device of the comparative example shown in FIG. It is assumed that the refrigeration cycle device 100 is in the heating operation before starting the operation procedure shown in FIG.
  • the control device 130 determines whether or not the temperature Te of the refrigerant is equal to or higher than the temperature threshold value T0 (step S1001). In step S1001, the control device 130 determines that frost has adhered to the heat source side heat exchanger 15 when the temperature Te of the refrigerant becomes equal to or lower than the temperature threshold value T0, and controls the flow path switching device 5 to switch the flow path ( Step S1002). As a result, the refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 15 via the flow path switching device 5.
  • the control device 130 determines whether or not the temperature Tr of the refrigerant is equal to or higher than the temperature threshold value Tc (step S1003).
  • step S1003 when the temperature Tr of the refrigerant becomes equal to or higher than the temperature threshold value Tc, the control device 130 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and controls the flow path switching device 5 to switch the flow path. (Step S1004).
  • the operation mode of the refrigeration cycle device 100 returns from the defrosting operation to the heating operation.
  • the gas refrigerant flows into the central portion of the first gas header 61 from the first gas pipe 43a.
  • the gas refrigerant that has flowed into the first gas header 61 is diverted to the plurality of heat transfer tubes 45a, but due to the pressure loss, the refrigerant tends to stay in the heat transfer tubes 45a on the lower stage side of the first heat source side heat exchanger 3.
  • the second heat source side heat exchanger 4 shown in FIG. 14 also has a refrigerant in the heat transfer tube 45b on the lower stage side of the second heat source side heat exchanger 4 during the defrosting operation. Is likely to stay.
  • FIG. 17 is a graph showing an example of the relationship between the flow rate of the refrigerant and the position of the heat exchanger on the heat source side during the defrosting operation.
  • the horizontal axis of FIG. 17 shows the flow rate of the refrigerant
  • the vertical axis shows the height Hu of the heat transfer tube 45a in the vertical direction (Z-axis arrow direction) of the first heat source side heat exchanger 3 shown in FIG.
  • the height of the lowermost heat transfer tube 45a is Hu1
  • the height of the uppermost heat transfer tube 45a is Hun. ..
  • FIG. 17 shows an example of the relationship between the flow rate of the refrigerant and the position of the heat exchanger on the heat source side during the defrosting operation.
  • the horizontal axis of FIG. 17 shows the flow rate of the refrigerant
  • the vertical axis shows the height Hu of the heat transfer tube 45a in the vertical direction (Z-axis arrow direction) of the first heat source side heat exchanger 3 shown in FIG.
  • the solid line graph is the case of the refrigeration cycle device 1d of the second embodiment, and the broken line graph is the case of the refrigeration cycle device 100 of the comparative example shown in FIG. Further, since the second heat source side heat exchanger 4 has the same tendency as the graph shown in FIG. 17, the description of the second heat source side heat exchanger 4 will be omitted here.
  • the heat exchange on the heat source side is shown as shown in the graph of the broken line in FIG.
  • the flow rate of the refrigerant on the lower stage side is smaller than that on the upper stage side in the vessel 15. This is because, as described with reference to FIGS. 13 and 14, when the refrigerant flows from the central portion of the header to the plurality of heat transfer tubes, the flow of the refrigerant becomes stagnant due to the pressure loss, and the refrigerant flows on the lower side. This is because it tends to stay.
  • the refrigeration cycle device 100 of the comparative example it takes a long time to complete the defrosting of the heat source side heat exchanger 15 in consideration of the flow rate of the refrigerant flowing through the lower heat transfer tube of the heat source side heat exchanger 15. It is required and the temperature threshold Tc is set to a high value. As a result, as shown in the broken line graph of FIG. 17, the refrigerant flows wastefully on the upper side until the defrosting of the heat transfer tube on the lower side of the heat source side heat exchanger 15 is completed.
  • the refrigerant flow rate has an influence on the difference in the height of the heat transfer tube 45a in the first heat source side heat exchanger 3. Is smaller than that of the comparative example, and the refrigerant is evenly distributed by the plurality of heat transfer tubes 45a. Therefore, the temperature threshold value Tb can be set to a temperature lower than the temperature threshold value Tc, and defrosting can be performed more efficiently than in the comparative example.
  • the first gas header 61 that divides the refrigerant flowing into the first heat source side heat exchanger 3 into the plurality of heat transfer tubes 45a during the defrosting operation, and the second heat source side heat. It has a second gas header 63 that divides the refrigerant flowing into the exchanger 4 into the plurality of heat transfer tubes 45b.
  • the first gas pipe 43a is connected to the central portion of the first gas header 61 in the direction of gravity
  • the second gas pipe 43b is connected to the central portion of the second gas header 63 in the direction of gravity.
  • the first heat source side heat exchanger 3 and the second heat source side heat exchanger are adjusted by adjusting the opening degree of the on-off valve 7 as described in the first embodiment during the defrosting operation.
  • the flow rate of the refrigerant flowing in each of 4 increases.
  • the frost adhering to the lower side of the heat source side heat exchanger can be reliably and efficiently removed. Since the temperature thresholds Ta and Tb can be set to values smaller than the temperature threshold Tc of the comparative example, the defrosting time is shorter than that of the comparative example, and defrosting can be performed efficiently.
  • Embodiment 3 In the refrigeration cycle apparatus of the third embodiment, the number of heat transfer tubes of the first heat source side heat exchanger and the number of heat transfer tubes of the second heat source side heat exchanger are different.
  • the same components as those described in the first and second embodiments are designated by the same reference numerals, and detailed description thereof will be omitted.
  • FIG. 18 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device according to the third embodiment.
  • the refrigeration cycle device 1e has a heat source side unit 10e.
  • the first heat source side heat exchanger 3 provided in the heat source side unit 10e has a configuration in which the first divided heat exchanger 3-1 and the second divided heat exchanger 3-2 are connected in parallel.
  • the first gas pipe 43a is branched into gas branch pipes 43a-1 and 43-2.
  • the gas branch pipe 43a-1 is connected to the first split heat exchanger 3-1 and the gas branch pipe 43a-2 is connected to the second split heat exchanger 3-2.
  • the first liquid pipe 44a is branched into liquid branch pipes 44a-1 and 44a-2.
  • the liquid branch pipe 44a-1 is connected to the first split heat exchanger 3-1 and the liquid branch pipe 44a-2 is connected to the second split heat exchanger 3-2.
  • the first gas header 61 is provided on the gas branch pipe 43a-1 side, and the first liquid header 62 is provided on the liquid branch pipe 44a-1 side.
  • the first gas header 65 is provided on the gas branch pipe 43a-2 side, and the first liquid header 66 is provided on the liquid branch pipe 44a-2 side. Since the first gas header 65 has the same configuration as the first gas header 61 and the first liquid header 66 has the same configuration as the first liquid header 62, detailed description thereof will be omitted.
  • FIG. 19 is an external perspective view showing a configuration example of the heat source side unit shown in FIG.
  • FIG. 20 is an external perspective view of the heat source side unit shown in FIG. 18 when viewed from a direction different from that in the case of FIG.
  • the first split heat exchanger 3-1 and the second split heat exchanger 3-2 have the same height, which is the length in the direction perpendicular to the ground (Z-axis arrow direction), and the height is L1. And.
  • the height of the second heat source side heat exchanger 4 is L2
  • the heights L1 and L2 have a relationship of L2 ⁇ L1.
  • FIG. 21 is a schematic view showing the layout of the heat source side heat exchanger when the heat source side unit shown in FIG. 20 is viewed from above.
  • the shapes of the first split heat exchanger 3-1 and the second split heat exchanger 3-2 when viewed from above are L-shaped.
  • the shape of the second heat source side heat exchanger 4 when viewed from above is linear.
  • the first split heat exchanger 3-1 is L-shaped, but when the first split heat exchanger 3-1 is extended in a straight line, the first split heat exchanger 3-1
  • the linear length of the second heat source side heat exchanger 4 is equal to the linear length of the second heat source side heat exchanger 4.
  • FIG. 22 is a side view showing a configuration example of the first split heat exchanger shown in FIG. Since the second split heat exchanger 3-2 has the same configuration as the first split heat exchanger 3-1, the description shown in FIG. 22 is omitted. Further, FIG. 22 shows a state in which the L-shaped first split heat exchanger 3-1 shown in FIG. 21 is linearly extended.
  • FIG. 23 is a side view showing a configuration example of the second heat source side heat exchanger shown in FIG. In FIGS. 22 and 23, the X-axis and the Z-axis are shown in the drawings for convenience of explanation, but the X-axis arrows correspond to the X-axis arrows shown in FIGS. 19 and 20. It does not have to be.
  • the number of heat transfer tubes 45a of the first split heat exchanger 3-1 shown in FIG. 22 is 13.
  • the number of heat transfer tubes 45b of the second heat source side heat exchanger 4 shown in FIG. 23 is nine.
  • the number of heat transfer tubes 45a of the first split heat exchanger 3-1 is larger than the number of heat transfer tubes 45b of the second heat source side heat exchanger 4.
  • the ratio of the number of heat transfer tubes 45a of the first split heat exchanger 3-1 to the number of heat transfer tubes 45b of the second heat source side heat exchanger 4 is the height L1 of the first heat source side heat exchanger 3 and the second.
  • the ratio (L1: L2) of the heat source side heat exchanger 4 to the height L2 is close to 3: 2.
  • the first heat source side heat exchanger 3 and the second heat source side heat exchanger 3 For 4 compare the number of heat transfer tubes to be defrosted.
  • the number of heat transfer tubes 45a of the first split heat exchanger 3-1 is (3/2) times the number of heat transfer tubes 45b of the second heat source side heat exchanger 4 from the ratio of L1 / L2. Since the first split heat exchanger 3-1 and the second split heat exchanger 3-2 have the same number of heat transfer tubes 45a, the number of heat transfer tubes 45a of the first heat source side heat exchanger 3 is the second heat source side heat exchange.
  • FIGS. 22 and 22 This is three times the number of heat transfer tubes 45b of the vessel 4.
  • the number of heat transfer tubes 45a of the first split heat exchanger 3-1 and the second split heat exchanger 3-2 and the number of heat transfer tubes 45b of the second heat source side heat exchanger 4 are shown in FIGS. 22 and 22. It is not limited to the case shown in 23.
  • the on-off valve 7 since the on-off valve 7 is closed from the start of the defrosting operation by the process of step S102 until the time t1 reaches the time threshold value tth1, the defrosting of the first heat source side heat exchanger 3 is concentrated. Is done. After that, the on-off valve 7 opens, and defrosting of the second heat source side heat exchanger 4 is disclosed, but the refrigerant also flows to the first heat source side heat exchanger 3. The amount of the refrigerant flowing through the first heat source side heat exchanger 3 is larger than the amount of the refrigerant flowing through the second heat source side heat exchanger 4.
  • the refrigeration cycle device 1e is the second heat source side heat exchanger.
  • the defrosting of the first heat source side heat exchanger 3 can be completed at the timing of the completion of defrosting of 4.
  • the number of heat transfer tubes 45a of the first heat source side heat exchanger 3 is larger than the number of heat transfer tubes of the second heat source side heat exchanger 4. According to the third embodiment, since the amount of the refrigerant flowing in the first heat source side heat exchanger 3 is larger than the amount of the refrigerant flowing in the second heat source side heat exchanger 4, the second heat source side heat exchanger 4 The defrosting of the first heat source side heat exchanger 3 can be completed at the timing of the end of defrosting.
  • Modification example 4 The refrigeration cycle device of the modified example 4 is a case where the flow rate adjusting valve 9 is provided in the first liquid pipe 44a in the refrigerant circuits 60a and 60b shown in FIG.
  • the same components as those described with reference to FIGS. 18 to 23 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • FIG. 24 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the modified example 4.
  • the flow rate adjusting valve 9 is provided in the first liquid pipe 44a.
  • the operation of the refrigeration cycle device 1f is shown in FIG. 10 except that the timing of switching the defrost target is determined based on the time t1 measured by the timer 53 in step S207 shown in FIG. Since the procedure is the same, the detailed description thereof will be omitted.
  • the refrigerant temperature sensor 12 may be provided in the liquid pipe 47 near the confluence of the first liquid pipe 44a and the second liquid pipe 44b instead of the second liquid pipe 44b.
  • a valve for shutting off the flow of the refrigerant is provided in each of the liquid pipes of the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4.
  • the refrigeration cycle device 1f of the modified example 4 controls the opening and closing of each valve during the defrosting operation to first defrost the first heat source side heat exchanger 3, and then the remaining second heat source side heat exchanger 4 By defrosting, defrosting can be performed reliably and efficiently.
  • the third embodiment may be applied to the refrigeration cycle device 1 described in the first embodiment. .. Further, in each of the second and third embodiments, any of the modified examples 1 to 3 may be combined.

Abstract

This refrigeration cycle device includes: a compressor; an expansion valve; a load-side heat exchanger; a flow path switching device; a heat source-side heat exchanger including a first heat source-side heat exchanger and a second heat source-side heat exchanger connected in parallel between the flow path switching device and the expansion valve; an open/close valve that is for the refrigerant flowing during a defrosting operation, and that is provided on the downstream side of the second heat source-side heat exchanger; and a control device that, on the occasion of performing the defrosting operation, controls the flow path switching device such that the refrigerant discharged from the compressor flows into the heat source-side heat exchanger. The control device includes: a first defrosting means for switching the open/close valve from an opened state to a closed state when the defrosting operation is started; a determination means for determining the timing for switching the object to be defrosted; and a second defrosting means for switching the open/close valve from a closed state to an opened state in accordance with the timing determined by the determination means.

Description

冷凍サイクル装置Refrigeration cycle equipment
　本発明は、空調対象空間の空気を調和する冷凍サイクル装置に関する。 The present invention relates to a refrigeration cycle device that harmonizes the air in the air-conditioned space.
　従来の空気調和装置において、上下に配列され、内部に冷媒の通路が形成された複数の扁平管と、隣り合う扁平管の間を空気が流れる複数の通風路に区画する複数のフィンと、を有する熱交換器が知られている（例えば、特許文献１参照）。 In a conventional air conditioner, a plurality of flat pipes arranged one above the other and having a refrigerant passage formed therein, and a plurality of fins for partitioning into a plurality of ventilation passages through which air flows between adjacent flat pipes. A heat exchanger having a heat exchanger is known (see, for example, Patent Document 1).
　特許文献１に開示された熱交換器は、メイン熱交換部と、メイン熱交換部と上下方向の異なる位置に設けられ、メイン熱交換部と直列に接続されるサブ熱交換部とを有する。そして、メイン熱交換部には、メイン熱交換部の下流側に位置するサブ熱交換部よりも扁平管が多く設けられている。また、熱交換器の最下段の扁平管がサブ熱交換部よりも上流側のメイン熱交換器に設けられている。この構成により、除霜運転時に最下段の熱交換部に付着した霜を融かすのに必要な時間の短縮を図っている。 The heat exchanger disclosed in Patent Document 1 has a main heat exchange unit and a sub heat exchange unit provided at different positions in the vertical direction from the main heat exchange unit and connected in series with the main heat exchange unit. The main heat exchange section is provided with more flat tubes than the sub heat exchange section located on the downstream side of the main heat exchange section. Further, a flat tube at the bottom of the heat exchanger is provided in the main heat exchanger on the upstream side of the sub heat exchanger. With this configuration, the time required to melt the frost adhering to the heat exchange section at the bottom during the defrosting operation is shortened.
特開２０１９－１１９４１号公報JP-A-2019-11941
　特許文献１に開示された空気調和装置においては、除霜運転の際、圧縮機から吐出される冷媒は、メイン熱交換部を通過した後にサブ熱交換部に流入する。つまり、圧縮機から吐出される冷媒は、メイン熱交換部の除霜が終了した後も、サブ熱交換部に流入する前に、メイン熱交換部を流通する。そのため、冷媒の熱は、サブ熱交換部に到達する前に、除霜を必要としないメイン熱交換部において冷媒と空気とが熱交換され、無駄に放出されてしまうことになる。その結果、除霜を効率的に行うことができない。 In the air conditioner disclosed in Patent Document 1, the refrigerant discharged from the compressor during the defrosting operation flows into the sub heat exchange section after passing through the main heat exchange section. That is, the refrigerant discharged from the compressor flows through the main heat exchange section even after the defrosting of the main heat exchange section is completed and before it flows into the sub heat exchange section. Therefore, the heat of the refrigerant is wasted because the refrigerant and the air are heat-exchanged in the main heat exchange section that does not require defrosting before reaching the sub heat exchange section. As a result, defrosting cannot be performed efficiently.
　本発明は、上記のような課題を解決するためになされたもので、除霜を効率的に行うことができる冷凍サイクル装置を提供するものである。 The present invention has been made to solve the above problems, and provides a refrigeration cycle apparatus capable of efficiently defrosting.
　本発明に係る冷凍サイクル装置は、冷媒を圧縮して吐出する圧縮機と、前記冷媒を減圧して膨張させる膨張弁と、前記膨張弁と接続される負荷側熱交換器と、前記圧縮機および前記負荷側熱交換器と接続される流路切替装置と、前記流路切替装置と前記膨張弁との間において並列に接続される第１熱源側熱交換器および第２熱源側熱交換器を含む熱源側熱交換器と、除霜運転時に流通する前記冷媒の前記第２熱源側熱交換器の下流側に設けられた開閉弁と、前記除霜運転を行う際、前記圧縮機から吐出される前記冷媒が前記熱源側熱交換器に流入するように前記流路切替装置を制御する制御装置と、を有し、前記制御装置は、前記除霜運転が開始されるとき、前記開閉弁を開状態から閉状態に切り替える第１除霜手段と、除霜対象の切り替えのタイミングを決定する判定手段と、前記判定手段によって決定された前記タイミングにしたがって、前記開閉弁を閉状態から開状態に切り替える第２除霜手段と、を有するものである。 The refrigeration cycle apparatus according to the present invention includes a compressor that compresses and discharges a refrigerant, an expansion valve that depressurizes and expands the refrigerant, a load side heat exchanger connected to the expansion valve, the compressor, and the like. A flow path switching device connected to the load side heat exchanger, and a first heat source side heat exchanger and a second heat source side heat exchanger connected in parallel between the flow path switching device and the expansion valve. The heat source side heat exchanger including the refrigerant, the on-off valve provided on the downstream side of the second heat source side heat exchanger of the refrigerant flowing during the defrosting operation, and the on-off valve provided on the downstream side of the second heat source side heat exchanger are discharged from the compressor during the defrosting operation. It has a control device that controls the flow path switching device so that the refrigerant flows into the heat source side heat exchanger, and the control device opens the on-off valve when the defrosting operation is started. The on-off valve is changed from the closed state to the open state according to the first defrosting means for switching from the open state to the closed state, the determining means for determining the switching timing of the defrosting target, and the timing determined by the determining means. It has a second defrosting means for switching.
　本発明によれば、第１除霜手段は、除霜開始時に開閉弁を閉じるので、圧縮機から吐出された冷媒は、２つの熱源側熱交換器のうち、第１熱源側熱交換器に集中的に流れる。その後、第２除霜手段が開閉弁を開くと、冷媒の熱の多くが第２熱源側熱交換器の除霜に費やされる。そのため、直列に接続される２つの熱源側熱交換器を同時に除霜する場合よりも、冷媒の熱が無駄に消費されることが抑制される。その結果、２つの熱源側熱交換器を効率的に除霜することができる。 According to the present invention, since the first defrosting means closes the on-off valve at the start of defrosting, the refrigerant discharged from the compressor is transferred to the first heat source side heat exchanger of the two heat source side heat exchangers. It flows intensively. After that, when the second defrosting means opens the on-off valve, most of the heat of the refrigerant is spent on defrosting the second heat source side heat exchanger. Therefore, wasteful consumption of the heat of the refrigerant is suppressed as compared with the case where two heat source side heat exchangers connected in series are defrosted at the same time. As a result, the two heat source side heat exchangers can be efficiently defrosted.
実施の形態１に係る冷凍サイクル装置の一構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus which concerns on Embodiment 1. FIG. 図１に示した制御装置の一構成例を示す機能ブロック図である。It is a functional block diagram which shows one configuration example of the control device shown in FIG. 図２に示した制御装置の一構成例を示すハードウェア構成図である。It is a hardware configuration diagram which shows one configuration example of the control device shown in FIG. 図２に示した制御装置の別の構成例を示すハードウェア構成図である。It is a hardware configuration diagram which shows another configuration example of the control device shown in FIG. 図１に示した冷凍サイクル装置の動作手順の一例を示すフローチャートである。It is a flowchart which shows an example of the operation procedure of the refrigeration cycle apparatus shown in FIG. 変形例１の冷凍サイクル装置の一構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of modification 1. FIG. 変形例１における制御装置の一構成例を示す機能ブロック図である。It is a functional block diagram which shows one configuration example of the control device in modification 1. FIG. 変形例２の冷凍サイクル装置の一構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of the modification 2. 変形例２における制御装置の一構成例を示す機能ブロック図である。It is a functional block diagram which shows one configuration example of the control device in the modification 2. 図８に示した冷凍サイクル装置の動作手順の一例を示すフローチャートである。It is a flowchart which shows an example of the operation procedure of the refrigeration cycle apparatus shown in FIG. 変形例３の冷凍サイクル装置の一構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of the modification 3. 実施の形態２に係る冷凍サイクル装置の一構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus which concerns on Embodiment 2. FIG. 図１２に示した第１熱源側熱交換器の一構成例を示す側面図である。It is a side view which shows one configuration example of the 1st heat source side heat exchanger shown in FIG. 図１２に示した第２熱源側熱交換器の一構成例を示す側面図である。It is a side view which shows one configuration example of the 2nd heat source side heat exchanger shown in FIG. 比較例の冷凍サイクル装置の構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows the structural example of the refrigeration cycle apparatus of the comparative example. 図１５に示した比較例の冷凍サイクル装置の動作手順の一例を示すフローチャートである。It is a flowchart which shows an example of the operation procedure of the refrigeration cycle apparatus of the comparative example shown in FIG. 除霜運転時において、冷媒流量と熱源側熱交換器の位置との関係の一例を示すグラフである。It is a graph which shows an example of the relationship between the refrigerant flow rate and the position of a heat exchanger on a heat source side at the time of defrosting operation. 実施の形態３に係る冷凍サイクル装置の一構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus which concerns on Embodiment 3. FIG. 図１８に示した熱源側ユニットの一構成例を示す外観斜視図である。It is an external perspective view which shows one configuration example of the heat source side unit shown in FIG. 図１８に示した熱源側ユニットについて、図１９の場合と異なる方向から見たときの外観斜視図である。FIG. 8 is an external perspective view of the heat source side unit shown in FIG. 18 when viewed from a direction different from that in the case of FIG. 図２０に示した熱源側ユニットを上から見たときの熱源側熱交換器のレイアウトを示す模式図である。It is a schematic diagram which shows the layout of the heat source side heat exchanger when the heat source side unit shown in FIG. 20 is seen from the top. 図１９に示した第１分割熱交換器の一構成例を示す側面図である。It is a side view which shows one configuration example of the 1st division heat exchanger shown in FIG. 図２０に示した第２熱源側熱交換器の一構成例を示す側面図である。It is a side view which shows one configuration example of the 2nd heat source side heat exchanger shown in FIG. 変形例４の冷凍サイクル装置の一構成例を示す冷媒回路図である。It is a refrigerant circuit diagram which shows one configuration example of the refrigeration cycle apparatus of the modification 4.
実施の形態１．
　本実施の形態１の冷凍サイクル装置の構成を説明する。図１は、実施の形態１に係る冷凍サイクル装置の一構成例を示す冷媒回路図である。図１に示すように、冷凍サイクル装置１は、熱源側ユニット１０と、負荷側ユニット２０ａおよび２０ｂと、熱源側ユニット１０、負荷側ユニット２０ａおよび２０ｂに含まれる冷媒機器を制御する制御装置３０とを有する。図１は、冷凍サイクル装置１が負荷側ユニット２０ａおよび２０ｂの２台の負荷側ユニットを有する場合を示しているが、負荷側ユニットは１台であってもよく、３台以上であってもよい。 Embodiment 1.
The configuration of the refrigeration cycle apparatus of the first embodiment will be described. FIG. 1 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device according to the first embodiment. As shown in FIG. 1, the refrigeration cycle device 1 includes a heat source side unit 10, load side units 20a and 20b, and a control device 30 for controlling the heat source side unit 10 and the refrigerant equipment included in the load side units 20a and 20b. Has. FIG. 1 shows a case where the refrigeration cycle device 1 has two load- side units 20a and 20b, but the load-side unit may be one or three or more. Good.
　熱源側ユニット１０は、冷媒を圧縮して吐出する圧縮機２と、冷媒を外気と熱交換させる熱源側熱交換器１５と、流路切替装置５と、アキュムレータ６と、開閉弁７とを有する。熱源側熱交換器１５は、第１熱源側熱交換器３および第２熱源側熱交換器４を有する。負荷側ユニット２０ａは、冷媒を負荷側ユニット２０ａが設置される室内の空気と熱交換させる負荷側熱交換器２１ａと、冷媒を減圧して膨張させる膨張弁２２ａとを有する。負荷側ユニット２０ｂは、冷媒を負荷側ユニット２０ｂが設置される室内の空気と熱交換させる負荷側熱交換器２１ｂと、冷媒を減圧して膨張させる膨張弁２２ｂとを有する。 The heat source side unit 10 includes a compressor 2 that compresses and discharges the refrigerant, a heat source side heat exchanger 15 that exchanges heat with the outside air, a flow path switching device 5, an accumulator 6, and an on-off valve 7. .. The heat source side heat exchanger 15 includes a first heat source side heat exchanger 3 and a second heat source side heat exchanger 4. The load-side unit 20a includes a load-side heat exchanger 21a that exchanges heat with the air in the room where the load-side unit 20a is installed, and an expansion valve 22a that depressurizes and expands the refrigerant. The load-side unit 20b includes a load-side heat exchanger 21b that exchanges heat with the air in the room where the load-side unit 20b is installed, and an expansion valve 22b that depressurizes and expands the refrigerant.
　第１熱源側熱交換器３および第２熱源側熱交換器４は、流路切替装置５と膨張弁２２ａおよび２２ｂとの間に並列に接続されている。第１熱源側熱交換器３の２つの冷媒出入口のうち、一方の冷媒出入口は第１ガス配管４３ａと接続され、他方の冷媒出入口は第１液配管４４ａと接続されている。第２熱源側熱交換器４の２つの冷媒出入口のうち、一方の冷媒出入口は第２ガス配管４３ｂと接続され、他方の冷媒出入口は第２液配管４４ｂと接続されている。第１ガス配管４３ａおよび第２ガス配管４３ｂは、ガス配管４１に合流して流路切替装置５と接続されている。第１液配管４４ａおよび第２液配管４４ｂは、液配管４７に合流して膨張弁２２ａおよび２２ｂと接続されている。開閉弁７は第２液配管４４ｂに設けられている。 The first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 are connected in parallel between the flow path switching device 5 and the expansion valves 22a and 22b. Of the two refrigerant inlets / outlets of the first heat source side heat exchanger 3, one refrigerant inlet / outlet is connected to the first gas pipe 43a, and the other refrigerant inlet / outlet is connected to the first liquid pipe 44a. Of the two refrigerant inlets / outlets of the second heat source side heat exchanger 4, one refrigerant inlet / outlet is connected to the second gas pipe 43b, and the other refrigerant inlet / outlet is connected to the second liquid pipe 44b. The first gas pipe 43a and the second gas pipe 43b join the gas pipe 41 and are connected to the flow path switching device 5. The first liquid pipe 44a and the second liquid pipe 44b join the liquid pipe 47 and are connected to the expansion valves 22a and 22b. The on-off valve 7 is provided in the second liquid pipe 44b.
　流路切替装置５は、冷媒配管４２を介して負荷側熱交換器２１ａおよび２１ｂと接続され、冷媒配管４８を介してアキュムレータ６と接続されている。また、流路切替装置５は、冷媒配管４９を介して、圧縮機２およびアキュムレータ６と接続されている。アキュムレータ６は圧縮機２の冷媒吸込口と接続されている。圧縮機２と、第１熱源側熱交換器３および第２熱源側熱交換器４と、膨張弁２２ａと、負荷側熱交換器２１ａとが冷媒配管４２等の配管で接続され、冷媒回路６０ａが構成される。また、圧縮機２と、第１熱源側熱交換器３および第２熱源側熱交換器４と、膨張弁２２ｂと、負荷側熱交換器２１ｂとが冷媒配管４２等の配管で接続され、冷媒回路６０ｂが構成される。 The flow path switching device 5 is connected to the load side heat exchangers 21a and 21b via the refrigerant pipe 42, and is connected to the accumulator 6 via the refrigerant pipe 48. Further, the flow path switching device 5 is connected to the compressor 2 and the accumulator 6 via the refrigerant pipe 49. The accumulator 6 is connected to the refrigerant suction port of the compressor 2. The compressor 2, the first heat source side heat exchanger 3, the second heat source side heat exchanger 4, the expansion valve 22a, and the load side heat exchanger 21a are connected by a pipe such as a refrigerant pipe 42, and the refrigerant circuit 60a Is configured. Further, the compressor 2, the first heat source side heat exchanger 3, the second heat source side heat exchanger 4, the expansion valve 22b, and the load side heat exchanger 21b are connected by a pipe such as a refrigerant pipe 42, and the refrigerant is used. The circuit 60b is configured.
　第２熱源側熱交換器４には、冷媒の温度Ｔｅを検出する熱交換器温度センサ１１が設けられている。第２液配管４４ｂには、第２液配管４４ｂを流通する冷媒の温度Ｔｎ２を検出する冷媒温度センサ１２が設けられている。負荷側ユニット２０ａには、負荷側ユニット２０ａが設置された室内の空気の温度を検出する室温センサ２３ａが設けられている。負荷側ユニット２０ｂには、負荷側ユニット２０ｂが設置された室内の空気の温度を検出する室温センサ２３ｂが設けられている。熱交換器温度センサ１１と、冷媒温度センサ１２と、室温センサ２３ａおよび２３ｂとは、例えば、サーミスタである。熱交換器温度センサ１１は、第２熱源側熱交換器４の代わりに、第１熱源側熱交換器３側に設けられていてもよい。 The second heat source side heat exchanger 4 is provided with a heat exchanger temperature sensor 11 that detects the temperature Te of the refrigerant. The second liquid pipe 44b is provided with a refrigerant temperature sensor 12 that detects the temperature Tn2 of the refrigerant flowing through the second liquid pipe 44b. The load-side unit 20a is provided with a room temperature sensor 23a that detects the temperature of the air in the room in which the load-side unit 20a is installed. The load-side unit 20b is provided with a room temperature sensor 23b that detects the temperature of the air in the room in which the load-side unit 20b is installed. The heat exchanger temperature sensor 11, the refrigerant temperature sensor 12, and the room temperature sensors 23a and 23b are, for example, thermistors. The heat exchanger temperature sensor 11 may be provided on the first heat source side heat exchanger 3 side instead of the second heat source side heat exchanger 4.
　圧縮機２は、容量を変えることができる圧縮機であり、例えば、インバータ圧縮機である。アキュムレータ６は圧縮機２に液冷媒が吸い込まれるのを防ぐ容器である。膨張弁２２ａおよび２２ｂは、例えば、電子膨張弁である。流路切替装置５は、圧縮機２から吐出される冷媒の流通方向を、ガス配管４１または冷媒配管４２に切り替える。流路切替装置５は、例えば、四方弁である。開閉弁７は、例えば、閉状態および開状態のうち、一方の状態から他方の状態に切り替えることができる遮断弁である。開閉弁７は、流通する冷媒の流量を調整する電子膨張弁であってもよい。第１熱源側熱交換器３および第２熱源側熱交換器４と、負荷側熱交換器２１ａおよび２１ｂとは、例えば、フィンアンドチューブ型熱交換器である。 The compressor 2 is a compressor whose capacity can be changed, for example, an inverter compressor. The accumulator 6 is a container that prevents the liquid refrigerant from being sucked into the compressor 2. The expansion valves 22a and 22b are, for example, electronic expansion valves. The flow path switching device 5 switches the flow direction of the refrigerant discharged from the compressor 2 to the gas pipe 41 or the refrigerant pipe 42. The flow path switching device 5 is, for example, a four-way valve. The on-off valve 7 is, for example, a shutoff valve capable of switching from one of the closed state and the open state to the other state. The on-off valve 7 may be an electronic expansion valve that adjusts the flow rate of the flowing refrigerant. The first heat source side heat exchanger 3, the second heat source side heat exchanger 4, and the load side heat exchangers 21a and 21b are, for example, fin-and-tube heat exchangers.
　制御装置３０は、図に示さない信号線を介して、圧縮機２と、流路切替装置５と、膨張弁２２ａおよび２２ｂと、開閉弁７との各機器と接続される。また、制御装置３０は、図に示さない信号線を介して、室温センサ２３ａおよび２３ｂと、熱交換器温度センサ１１と、冷媒温度センサ１２との各センサと接続される。制御装置３０と、圧縮機２、流路切替装置５、膨張弁２２ａ、膨張弁２２ｂおよび開閉弁７の各機器との通信接続は、有線に限らず、無線であってもよい。センサに関しても、制御装置３０と、室温センサ２３ａ、室温センサ２３ｂ、熱交換器温度センサ１１および冷媒温度センサ１２の各センサとの通信接続は、有線に限らず、無線であってもよい。 The control device 30 is connected to each device of the compressor 2, the flow path switching device 5, the expansion valves 22a and 22b, and the on-off valve 7 via a signal line (not shown in the figure). Further, the control device 30 is connected to each of the room temperature sensors 23a and 23b, the heat exchanger temperature sensor 11, and the refrigerant temperature sensor 12 via signal lines (not shown in the figure). The communication connection between the control device 30 and each device of the compressor 2, the flow path switching device 5, the expansion valve 22a, the expansion valve 22b, and the on-off valve 7 is not limited to the wired connection, but may be wireless. Regarding the sensors, the communication connection between the control device 30 and each of the room temperature sensor 23a, the room temperature sensor 23b, the heat exchanger temperature sensor 11 and the refrigerant temperature sensor 12 is not limited to wired, but may be wireless.
　図１に示す制御装置３０の構成について説明する前に、冷凍サイクル装置１の各運転モードにおける冷媒の流れを簡単に説明する。ここでは、冷媒回路６０ａの場合について説明する。また、開閉弁７は開状態であるものとする。 Before explaining the configuration of the control device 30 shown in FIG. 1, the flow of the refrigerant in each operation mode of the refrigeration cycle device 1 will be briefly described. Here, the case of the refrigerant circuit 60a will be described. Further, it is assumed that the on-off valve 7 is in the open state.
　［冷房運転］
　はじめに、図１を参照して、冷凍サイクル装置１が冷房運転を行う場合の冷媒の流れを説明する。冷凍サイクル装置１が冷房運転を行う場合、制御装置３０は、圧縮機２から吐出される冷媒が第１熱源側熱交換器３および第２熱源側熱交換器４に流入するように、流路切替装置５の流路を切り替える。低温低圧の冷媒が圧縮機２によって圧縮されることで、高温高圧のガス冷媒が圧縮機２から吐出される。圧縮機２から吐出されたガス冷媒は、流路切替装置５を経由して、第１熱源側熱交換器３および第２熱源側熱交換器４に流入する。第１熱源側熱交換器３および第２熱源側熱交換器４に流入した冷媒は、これら並列に接続された熱交換器において、空気と熱交換することで凝縮し、低温高圧の液冷媒となって、第１熱源側熱交換器３および第２熱源側熱交換器４から流出する。 [Cooling operation]
First, with reference to FIG. 1, the flow of the refrigerant when the refrigeration cycle device 1 performs the cooling operation will be described. When the refrigeration cycle device 1 performs the cooling operation, the control device 30 flows through the flow path so that the refrigerant discharged from the compressor 2 flows into the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4. The flow path of the switching device 5 is switched. When the low-temperature and low-pressure refrigerant is compressed by the compressor 2, the high-temperature and high-pressure gas refrigerant is discharged from the compressor 2. The gas refrigerant discharged from the compressor 2 flows into the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 via the flow path switching device 5. The refrigerant flowing into the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 condenses by exchanging heat with air in these heat exchangers connected in parallel, and becomes a low-temperature and high-pressure liquid refrigerant. Then, it flows out from the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4.
　第１熱源側熱交換器３および第２熱源側熱交換器４から流出した液冷媒は、膨張弁２２ａによって低温低圧の液冷媒になる。液冷媒は、負荷側熱交換器２１ａに流入する。負荷側熱交換器２１ａに流入した冷媒は、負荷側熱交換器２１ａにおいて、空気と熱交換することで蒸発し、低温低圧のガス冷媒となって負荷側熱交換器２１ａから流出する。負荷側熱交換器２１ａにおいて、冷媒が室内の空気から吸熱することで、室内の空気が冷却される。負荷側熱交換器２１ａから流出した冷媒は、流路切替装置５を介して圧縮機２に吸入される。冷房運転の間、圧縮機２から吐出される冷媒が第１熱源側熱交換器３および第２熱源側熱交換器４と、膨張弁２２ａと、負荷側熱交換器２１ａとを順に流通した後、圧縮機２に吸引されるまでのサイクルが繰り返される。 The liquid refrigerant flowing out from the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 becomes a low-temperature low-pressure liquid refrigerant by the expansion valve 22a. The liquid refrigerant flows into the load side heat exchanger 21a. The refrigerant that has flowed into the load-side heat exchanger 21a evaporates by exchanging heat with air in the load-side heat exchanger 21a, becomes a low-temperature low-pressure gas refrigerant, and flows out of the load-side heat exchanger 21a. In the load side heat exchanger 21a, the air in the room is cooled by the refrigerant absorbing heat from the air in the room. The refrigerant flowing out of the load-side heat exchanger 21a is sucked into the compressor 2 via the flow path switching device 5. During the cooling operation, after the refrigerant discharged from the compressor 2 circulates in order through the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4, the expansion valve 22a, and the load side heat exchanger 21a. , The cycle until it is sucked into the compressor 2 is repeated.
　［暖房運転］
　次に、図１を参照して、冷凍サイクル装置１が暖房運転を行う場合の冷媒の流れを説明する。冷凍サイクル装置１が暖房運転を行う場合、制御装置３０は、圧縮機２から吐出される冷媒が負荷側熱交換器２１ａに流入するように、流路切替装置５の流路を切り替える。低温低圧の冷媒が圧縮機２によって圧縮されることで、高温高圧のガス冷媒が圧縮機２から吐出される。圧縮機２から吐出された高温高圧のガス冷媒は、流路切替装置５を経由して、負荷側熱交換器２１ａに流入する。負荷側熱交換器２１ａに流入した冷媒は、負荷側熱交換器２１ａにおいて、空気と熱交換することで凝縮され、高温高圧の液冷媒となって負荷側熱交換器２１ａから流出する。負荷側熱交換器２１ａにおいて、冷媒が室内の空気に放熱することで、室内の空気が暖められる。 [Heating operation]
Next, with reference to FIG. 1, the flow of the refrigerant when the refrigeration cycle device 1 performs the heating operation will be described. When the refrigeration cycle device 1 performs the heating operation, the control device 30 switches the flow path of the flow path switching device 5 so that the refrigerant discharged from the compressor 2 flows into the load side heat exchanger 21a. When the low-temperature and low-pressure refrigerant is compressed by the compressor 2, the high-temperature and high-pressure gas refrigerant is discharged from the compressor 2. The high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the load-side heat exchanger 21a via the flow path switching device 5. The refrigerant flowing into the load-side heat exchanger 21a is condensed by exchanging heat with air in the load-side heat exchanger 21a, becomes a high-temperature and high-pressure liquid refrigerant, and flows out from the load-side heat exchanger 21a. In the load side heat exchanger 21a, the air in the room is warmed by the refrigerant dissipating heat to the air in the room.
　負荷側熱交換器２１ａから流出した高温高圧の液冷媒は、膨張弁２２ａによって低温低圧の液冷媒になる。液冷媒は、第１熱源側熱交換器３および第２熱源側熱交換器４に流入する。第１熱源側熱交換器３および第２熱源側熱交換器４において、冷媒は空気と熱交換することで蒸発し、低温低圧のガス冷媒となって、第１熱源側熱交換器３および第２熱源側熱交換器４から流出する。第１熱源側熱交換器３および第２熱源側熱交換器４から流出した冷媒は、流路切替装置５を介して圧縮機２に吸入される。冷凍サイクル装置１が暖房運転を行っている間、圧縮機２から吐出される冷媒が、負荷側熱交換器２１ａと、膨張弁２２ａと、第１熱源側熱交換器３および第２熱源側熱交換器４とを順に流通した後、圧縮機２に吸引されるまでのサイクルが繰り返される。 The high temperature and high pressure liquid refrigerant flowing out from the load side heat exchanger 21a becomes a low temperature and low pressure liquid refrigerant by the expansion valve 22a. The liquid refrigerant flows into the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4. In the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4, the refrigerant evaporates by exchanging heat with air to become a low-temperature low-pressure gas refrigerant, and becomes the first heat source side heat exchanger 3 and the first heat exchanger. 2 Outflow from the heat source side heat exchanger 4. The refrigerant flowing out from the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 is sucked into the compressor 2 via the flow path switching device 5. While the refrigeration cycle device 1 is performing the heating operation, the refrigerant discharged from the compressor 2 is the load side heat exchanger 21a, the expansion valve 22a, the first heat source side heat exchanger 3, and the second heat source side heat. After circulating the exchanger 4 in order, the cycle until it is sucked into the compressor 2 is repeated.
［除霜運転］
　図１を参照して、冷凍サイクル装置１が除霜運転を行う場合の冷媒の流れを説明する。冷凍サイクル装置１が運転モードを暖房運転から除霜運転に切り替える場合、制御装置３０は、圧縮機２から吐出される冷媒が第１熱源側熱交換器３および第２熱源側熱交換器４に流入するように、流路切替装置５の流路を切り替える。また、制御装置３０は、膨張弁２２ａを全開状態に制御する。除霜運転の場合、冷媒回路６０ａにおける冷媒の流通方向は冷房運転の場合と同じになるため、冷媒の流れについての詳細な説明を省略する。 [Defrosting operation]
With reference to FIG. 1, the flow of the refrigerant when the refrigeration cycle device 1 performs the defrosting operation will be described. When the refrigeration cycle device 1 switches the operation mode from the heating operation to the defrosting operation, the control device 30 sends the refrigerant discharged from the compressor 2 to the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4. The flow path of the flow path switching device 5 is switched so as to flow in. Further, the control device 30 controls the expansion valve 22a to the fully open state. In the case of the defrosting operation, the flow direction of the refrigerant in the refrigerant circuit 60a is the same as in the case of the cooling operation, and therefore detailed description of the flow of the refrigerant will be omitted.
　次に、図１に示した制御装置３０の構成を説明する。図２は、図１に示した制御装置の一構成例を示す機能ブロック図である。 Next, the configuration of the control device 30 shown in FIG. 1 will be described. FIG. 2 is a functional block diagram showing a configuration example of the control device shown in FIG.
　制御装置３０は、冷凍サイクル制御手段５１と、判定手段５２と、タイマ５３と、第１除霜手段５４と、第２除霜手段５５とを有する。制御装置３０は、マイクロコンピュータなどの演算装置がソフトウェアを実行することにより各種機能が実現される。また、制御装置３０は、各種機能を実現する回路デバイスなどのハードウェアで構成されてもよい。設定温度Ｔｓ１が、負荷側ユニット２０ａを利用するユーザによって、図に示さないリモートコントローラを介して制御装置３０に入力される。設定温度Ｔｓ２が、負荷側ユニット２０ｂを利用するユーザによって、図に示さないリモートコントローラを介して制御装置３０に入力される。なお、図１に示した冷凍サイクル装置１において、制御装置３０の設置位置は限定されず、制御装置３０は、熱源側ユニット１０に設けられてもよく、負荷側ユニット２０ａまたは２０ｂに設けられてもよい。 The control device 30 includes a refrigerating cycle control means 51, a determination means 52, a timer 53, a first defrosting means 54, and a second defrosting means 55. Various functions of the control device 30 are realized by executing software by an arithmetic unit such as a microcomputer. Further, the control device 30 may be composed of hardware such as a circuit device that realizes various functions. The set temperature Ts1 is input to the control device 30 by the user who uses the load side unit 20a via a remote controller (not shown). The set temperature Ts2 is input to the control device 30 by the user who uses the load side unit 20b via a remote controller (not shown). In the refrigeration cycle device 1 shown in FIG. 1, the installation position of the control device 30 is not limited, and the control device 30 may be provided in the heat source side unit 10 or in the load side unit 20a or 20b. May be good.
　冷凍サイクル制御手段５１は、冷凍サイクル装置１の運転モードに対応して流路切替装置５を制御する。冷凍サイクル制御手段５１は、室温センサ２３ａおよび２３ｂから受け取る検出値と設定温度Ｔｓ１およびＴｓ２とに基づいて、圧縮機２の運転周波数と、膨張弁２２ａおよび２２ｂの開度とを制御する。具体的には、冷凍サイクル制御手段５１は、室温センサ２３ａの検出値が設定温度Ｔｓ１に近づくように、室温センサ２３ｂの検出値が設定温度Ｔｓ２に近づくように、圧縮機２の運転周波数と、膨張弁２２ａおよび２２ｂの開度とを制御する。 The refrigeration cycle control means 51 controls the flow path switching device 5 according to the operation mode of the refrigeration cycle device 1. The refrigeration cycle control means 51 controls the operating frequency of the compressor 2 and the opening degrees of the expansion valves 22a and 22b based on the detected values received from the room temperature sensors 23a and 23b and the set temperatures Ts1 and Ts2. Specifically, the refrigeration cycle control means 51 sets the operating frequency of the compressor 2 and the operating frequency of the compressor 2 so that the detected value of the room temperature sensor 23a approaches the set temperature Ts1 and the detected value of the room temperature sensor 23b approaches the set temperature Ts2. The opening degrees of the expansion valves 22a and 22b are controlled.
　冷凍サイクル装置１の暖房運転中に、冷凍サイクル制御手段５１は、熱交換器温度センサ１１から受信する冷媒の温度Ｔｅを監視し、冷媒の温度Ｔｅが予め決められた温度閾値Ｔ０以下であるか否かを判定する。温度閾値Ｔ０は、例えば、０℃である。冷凍サイクル制御手段５１は、冷媒の温度Ｔｅが温度閾値Ｔ０以下になると、流路切替装置５を制御して流路を切り替えるとともに、除霜運転を開始したことを示す除霜開始情報を判定手段５２に送信する。冷凍サイクル制御手段５１は、除霜終了情報を判定手段５２から受信すると、流路切替装置５を制御して流路を切り替え、運転モードを除霜運転から暖房運転に切り替える。 During the heating operation of the refrigeration cycle device 1, the refrigeration cycle control means 51 monitors the temperature Te of the refrigerant received from the heat exchanger temperature sensor 11, and whether the temperature Te of the refrigerant is equal to or less than a predetermined temperature threshold T0. Judge whether or not. The temperature threshold T0 is, for example, 0 ° C. When the temperature Te of the refrigerant becomes equal to or lower than the temperature threshold value T0, the refrigerating cycle control means 51 controls the flow path switching device 5 to switch the flow path and determines the defrosting start information indicating that the defrosting operation is started. Send to 52. When the refrigerating cycle control means 51 receives the defrosting end information from the determining means 52, the refrigerating cycle control means 51 controls the flow path switching device 5 to switch the flow path, and switches the operation mode from the defrosting operation to the heating operation.
　タイマ５３は、時間を計測し、計測時間の情報を判定手段５２に提供する。判定手段５２は、除霜開始から経過する時間と冷媒温度センサ１２が検出する冷媒の温度Ｔｎ２とのうち、少なくともいずれかの値に基づいて、除霜対象の切り替えのタイミングを決定する。判定手段５２は、冷凍サイクル制御手段５１から除霜開始情報を受信すると、除霜開始情報を第１除霜手段５４に転送するとともに、除霜開始からの経過時間である時間ｔ１を監視する。判定手段５２は、時間ｔ１が予め決められた時間閾値ｔｔｈ１以上であるか否かを判定する。時間閾値ｔｔｈ１は、第１熱源側熱交換器３の除霜が完全に終了する前の時間に設定されている。判定手段５２は、時間ｔ１が時間閾値ｔｔｈ１以上になると、開閉弁７の状態の切り替えを指示する旨の切替指示情報を第２除霜手段５５に送信する。 The timer 53 measures the time and provides the measurement time information to the determination means 52. The determination means 52 determines the timing of switching the defrost target based on at least one of the time elapsed from the start of defrosting and the temperature Tn2 of the refrigerant detected by the refrigerant temperature sensor 12. When the determination means 52 receives the defrosting start information from the refrigeration cycle control means 51, the determination means 52 transfers the defrosting start information to the first defrosting means 54 and monitors the time t1 which is the elapsed time from the defrosting start. The determination means 52 determines whether or not the time t1 is equal to or greater than a predetermined time threshold value tth1. The time threshold value tth1 is set to the time before the defrosting of the first heat source side heat exchanger 3 is completely completed. When the time t1 becomes equal to or higher than the time threshold value tth1, the determination means 52 transmits switching instruction information to instruct the switching of the state of the on-off valve 7 to the second defrosting means 55.
　また、判定手段５２は、切替指示情報を第２除霜手段５５に送信した後、冷媒温度センサ１２から受信する冷媒の温度Ｔｎ２を監視し、冷媒の温度Ｔｎ２が予め決められた温度閾値Ｔｂ以上であるか否かを判定する。温度閾値Ｔｂは、例えば、７℃である。判定手段５２は、冷媒の温度Ｔｎ２が温度閾値Ｔｂ以上になると、除霜が終了したことを示す除霜終了情報を冷凍サイクル制御手段５１に送信する。 Further, the determination means 52 monitors the refrigerant temperature Tn2 received from the refrigerant temperature sensor 12 after transmitting the switching instruction information to the second defrosting means 55, and the refrigerant temperature Tn2 is equal to or higher than a predetermined temperature threshold value Tb. It is determined whether or not it is. The temperature threshold Tb is, for example, 7 ° C. When the temperature Tn2 of the refrigerant becomes equal to or higher than the temperature threshold value Tb, the determination means 52 transmits the defrosting end information indicating that the defrosting is completed to the refrigerating cycle control means 51.
　第１除霜手段５４は、除霜開始情報を判定手段５２から受信すると、開閉弁７を開状態から閉状態に切り替える。第２除霜手段５５は、切替指示情報を判定手段５２から受信すると、開閉弁７を閉状態から開状態に切り替える。 When the first defrosting means 54 receives the defrosting start information from the determining means 52, the first defrosting means 54 switches the on-off valve 7 from the open state to the closed state. When the second defrosting means 55 receives the switching instruction information from the determining means 52, the second defrosting means 55 switches the on-off valve 7 from the closed state to the open state.
　ここで、図２に示した制御装置３０のハードウェアの一例を説明する。図３は、図２に示した制御装置の一構成例を示すハードウェア構成図である。制御装置３０の各種機能がハードウェアで実行される場合、図２に示した制御装置３０は、図３に示すように、処理回路３１で構成される。図２に示した、冷凍サイクル制御手段５１、判定手段５２、タイマ５３、第１除霜手段５４および第２除霜手段５５の各機能は、処理回路３１により実現される。 Here, an example of the hardware of the control device 30 shown in FIG. 2 will be described. FIG. 3 is a hardware configuration diagram showing a configuration example of the control device shown in FIG. When various functions of the control device 30 are executed by hardware, the control device 30 shown in FIG. 2 is composed of a processing circuit 31 as shown in FIG. Each function of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54, and the second defrosting means 55 shown in FIG. 2 is realized by the processing circuit 31.
　各機能がハードウェアで実行される場合、処理回路３１は、例えば、単一回路、複合回路、プログラム化したプロセッサ、並列プログラム化したプロセッサ、ＡＳＩＣ（Ａｐｐｌｉｃａｔｉｏｎ　Ｓｐｅｃｉｆｉｃ　Ｉｎｔｅｇｒａｔｅｄ　Ｃｉｒｃｕｉｔ）、ＦＰＧＡ（Ｆｉｅｌｄ－Ｐｒｏｇｒａｍｍａｂｌｅ　Ｇａｔｅ　Ａｒｒａｙ）、または、これらを組み合わせたものに該当する。冷凍サイクル制御手段５１、判定手段５２、タイマ５３、第１除霜手段５４および第２除霜手段５５の各手段の機能のそれぞれを処理回路３１で実現してもよく、各手段の機能を１つの処理回路３１で実現してもよい。 When each function is executed by hardware, the processing circuit 31 may be, for example, a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC (Application Specific Integrated Circuit), or an FPGA (Field-Programmable Gate). It corresponds to Array) or a combination of these. Each of the functions of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54 and the second defrosting means 55 may be realized by the processing circuit 31, and the function of each means may be 1 It may be realized by one processing circuit 31.
　また、図２に示した制御装置３０の別のハードウェアの一例を説明する。図４は、図２に示した制御装置の別の構成例を示すハードウェア構成図である。制御装置３０の各種機能がソフトウェアで実行される場合、図２に示した制御装置３０は、図４に示すように、プロセッサ７１およびメモリ７２で構成される。冷凍サイクル制御手段５１、判定手段５２、タイマ５３、第１除霜手段５４および第２除霜手段５５の各機能は、プロセッサ７１およびメモリ７２により実現される。図４は、プロセッサ７１およびメモリ７２が互いに通信可能に接続されることを示している。 Further, an example of another hardware of the control device 30 shown in FIG. 2 will be described. FIG. 4 is a hardware configuration diagram showing another configuration example of the control device shown in FIG. When various functions of the control device 30 are executed by software, the control device 30 shown in FIG. 2 includes a processor 71 and a memory 72 as shown in FIG. The functions of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54, and the second defrosting means 55 are realized by the processor 71 and the memory 72. FIG. 4 shows that the processor 71 and the memory 72 are communicably connected to each other.
　各機能がソフトウェアで実行される場合、冷凍サイクル制御手段５１、判定手段５２、タイマ５３、第１除霜手段５４および第２除霜手段５５の機能は、ソフトウェア、ファームウェア、またはソフトウェアとファームウェアとの組み合わせにより実現される。ソフトウェアおよびファームウェアは、プログラムとして記述され、メモリ７２に格納される。プロセッサ７１は、メモリ７２に記憶されたプログラムを読み出して実行することにより、各手段の機能を実現する。 When each function is executed by software, the functions of the refrigerating cycle control means 51, the determination means 52, the timer 53, the first defrosting means 54 and the second defrosting means 55 are software, firmware, or software and firmware. It is realized by the combination. The software and firmware are written as a program and stored in the memory 72. The processor 71 realizes the function of each means by reading and executing the program stored in the memory 72.
　メモリ７２として、例えば、ＲＯＭ（Ｒｅａｄ　Ｏｎｌｙ　Ｍｅｍｏｒｙ）、フラッシュメモリ、ＥＰＲＯＭ（Ｅｒａｓａｂｌｅ　ａｎｄ　Ｐｒｏｇｒａｍｍａｂｌｅ　ＲＯＭ）およびＥＥＰＲＯＭ（Ｅｌｅｃｔｒｉｃａｌｌｙ　Ｅｒａｓａｂｌｅ　ａｎｄ　Ｐｒｏｇｒａｍｍａｂｌｅ　ＲＯＭ）等の不揮発性の半導体メモリが用いられる。また、メモリ７２として、ＲＡＭ（Ｒａｎｄｏｍ　Ａｃｃｅｓｓ　Ｍｅｍｏｒｙ）の揮発性の半導体メモリが用いられてもよい。さらに、メモリ７２として、磁気ディスク、フレキシブルディスク、光ディスク、ＣＤ（Ｃｏｍｐａｃｔ　Ｄｉｓｃ）、ＭＤ（Ｍｉｎｉ　Ｄｉｓｃ）およびＤＶＤ（Ｄｉｇｉｔａｌ　Ｖｅｒｓａｔｉｌｅ　Ｄｉｓｃ）等の着脱可能な記録媒体が用いられてもよい。 As the memory 72, for example, a non-volatile semiconductor memory such as a ROM (Read Only Memory), a flash memory, an EPROM (Erasable and Programmable ROM) and an EPROM (Electrically Erasable and Programmable ROM) is used. Further, as the memory 72, a volatile semiconductor memory of RAM (Random Access Memory) may be used. Further, as the memory 72, a removable recording medium such as a magnetic disk, a flexible disk, an optical disk, a CD (Compact Disc), an MD (Mini Disc), or a DVD (Digital Versaille Disc) may be used.
　次に、本実施の形態１の冷凍サイクル装置１の動作を説明する。図５は、図１に示した冷凍サイクル装置の動作手順の一例を示すフローチャートである。図５は、冷凍サイクル装置１が除霜運転を行う場合の動作手順の一例を示す。冷凍サイクル装置１は図５に示す動作手順を開始する前、暖房運転を行っており、開閉弁７は開状態であるものとする。 Next, the operation of the refrigeration cycle device 1 of the first embodiment will be described. FIG. 5 is a flowchart showing an example of the operation procedure of the refrigeration cycle apparatus shown in FIG. FIG. 5 shows an example of an operation procedure when the refrigerating cycle device 1 performs a defrosting operation. It is assumed that the refrigerating cycle device 1 is in the heating operation before starting the operation procedure shown in FIG. 5, and the on-off valve 7 is in the open state.
　冷凍サイクル制御手段５１は、熱交換器温度センサ１１から受信する、冷媒の温度Ｔｅが温度閾値Ｔ０以下になったか否かを判定する（ステップＳ１０１）。冷凍サイクル制御手段５１は、ステップＳ１０１において、冷媒の温度Ｔｅが温度閾値Ｔ０以下になると、熱源側熱交換器１５に霜が付着したと判定し、流路切替装置５を制御して流路を切り替える（ステップＳ１０２）。これにより、圧縮機２から吐出される冷媒は、流路切替装置５を経由して熱源側熱交換器１５に流入する。また、冷凍サイクル制御手段５１は、ステップＳ１０２において、除霜開始情報を判定手段５２に送信する。 The refrigeration cycle control means 51 determines whether or not the temperature Te of the refrigerant received from the heat exchanger temperature sensor 11 is equal to or lower than the temperature threshold value T0 (step S101). In step S101, the refrigeration cycle control means 51 determines that frost has adhered to the heat source side heat exchanger 15 when the temperature Te of the refrigerant becomes equal to or lower than the temperature threshold value T0, and controls the flow path switching device 5 to control the flow path. Switching (step S102). As a result, the refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 15 via the flow path switching device 5. Further, the refrigeration cycle control means 51 transmits the defrosting start information to the determination means 52 in step S102.
　判定手段５２は、冷凍サイクル制御手段５１から除霜開始情報を受信すると、除霜開始情報を第１除霜手段５４に転送するとともに、タイマ５３によって計測される時間ｔ１を監視する。第１除霜手段５４は、除霜開始情報を判定手段５２から受信すると、開閉弁７を閉じる（ステップＳ１０３）。判定手段５２は、時間ｔ１が時間閾値ｔｔｈ１以上になったか否かを判定する（ステップＳ１０４）。判定手段５２は、ステップＳ１０４において、時間ｔ１が時間閾値ｔｔｈ１以上になると、切替指示情報を第２除霜手段５５に送信する。 When the determination means 52 receives the defrosting start information from the refrigerating cycle control means 51, the determination means 52 transfers the defrosting start information to the first defrosting means 54 and monitors the time t1 measured by the timer 53. When the first defrosting means 54 receives the defrosting start information from the determining means 52, the first defrosting means 54 closes the on-off valve 7 (step S103). The determination means 52 determines whether or not the time t1 is equal to or greater than the time threshold value tth1 (step S104). In step S104, the determination means 52 transmits the switching instruction information to the second defrosting means 55 when the time t1 becomes the time threshold value tth1 or more.
　第２除霜手段５５は、切替指示情報を判定手段５２から受信すると、開閉弁７を開く（ステップＳ１０５）。判定手段５２は、切替指示情報を第２除霜手段５５に送信した後、冷媒温度センサ１２から受信する、冷媒の温度Ｔｎ２が温度閾値Ｔｂ以上になったか否かを判定する（ステップＳ１０６）。判定手段５２は、冷媒の温度Ｔｎ２が温度閾値Ｔｂ以上になると、熱源側熱交換器１５の除霜が終了したと判定し、除霜終了情報を冷凍サイクル制御手段５１に送信する。 When the second defrosting means 55 receives the switching instruction information from the determining means 52, the on-off valve 7 is opened (step S105). After transmitting the switching instruction information to the second defrosting means 55, the determining means 52 determines whether or not the temperature Tn2 of the refrigerant received from the refrigerant temperature sensor 12 is equal to or higher than the temperature threshold value Tb (step S106). When the temperature Tn2 of the refrigerant becomes equal to or higher than the temperature threshold value Tb, the determination means 52 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and transmits the defrosting completion information to the refrigeration cycle control means 51.
　冷凍サイクル制御手段５１は、除霜終了情報を判定手段５２から受信すると、流路切替装置５を制御して流路を切り替える（ステップＳ１０７）。これにより、圧縮機２から吐出される冷媒は、流路切替装置５を経由して負荷側ユニット２０ａおよび２０ｂに流入する。冷凍サイクル装置１の運転モードが除霜運転から暖房運転に戻る。 When the refrigeration cycle control means 51 receives the defrosting end information from the determination means 52, the refrigeration cycle control means 51 controls the flow path switching device 5 to switch the flow path (step S107). As a result, the refrigerant discharged from the compressor 2 flows into the load- side units 20a and 20b via the flow path switching device 5. The operation mode of the refrigeration cycle device 1 returns from the defrosting operation to the heating operation.
　このようにして、冷凍サイクル装置１が除霜を開始してから時間ｔ１が時間閾値ｔｔｈ１に到達するまで、第１熱源側熱交換器３が集中的に除霜される。その後、冷凍サイクル装置１は、第１熱源側熱交換器３の除霜が完了する前に第２熱源側熱交換器４の除霜を開始するが、第１熱源側熱交換器３への冷媒の流通が継続される。その後、判定手段５２が第２熱源側熱交換器４の下流側の冷媒の温度Ｔｎ１によって第２熱源側熱交換器４の除霜が終了したか否かを判定する。第２熱源側熱交換器４の下流側の冷媒の温度によって第２熱源側熱交換器の除霜の完了が判定されたとき、第１熱源側熱交換器３の除霜も完了している。 In this way, the first heat source side heat exchanger 3 is intensively defrosted from the time when the refrigeration cycle device 1 starts defrosting until the time t1 reaches the time threshold value tth1. After that, the refrigeration cycle apparatus 1 starts defrosting the second heat source side heat exchanger 4 before the defrosting of the first heat source side heat exchanger 3 is completed, but the first heat source side heat exchanger 3 is defrosted. Refrigerant flow continues. After that, the determination means 52 determines whether or not the defrosting of the second heat source side heat exchanger 4 is completed by the temperature Tn1 of the refrigerant on the downstream side of the second heat source side heat exchanger 4. When the completion of defrosting of the second heat source side heat exchanger is determined by the temperature of the refrigerant on the downstream side of the second heat source side heat exchanger 4, the defrosting of the first heat source side heat exchanger 3 is also completed. ..
　なお、図１に示す構成例においては、冷媒温度センサ１２が第２液配管４４ｂに設けられているが、第１液配管４４ａおよび第２液配管４４ｂの合流点近くの液配管４７に冷媒温度センサ１２が設けられていてもよい。この場合、図５に示したステップＳ１０４においては、判定手段５２は、冷媒の温度Ｔｎ２が予め決められた温度閾値Ｔａ以上か否かを判定する。そして、ステップＳ１０４の判定の結果、判定手段５２は、冷媒の温度Ｔｎ２が温度閾値Ｔａ以上である場合、切替指示情報を第２除霜手段５５に送信すればよい。温度閾値ＴａおよびＴｂは、例えば、Ｔａ＞Ｔｂの関係である。Ｔａ＞Ｔｂの関係により第１熱源側熱交換器３の除霜が完全に終了する前に、冷凍サイクル装置１がステップＳ１０５の処理に進んでも、第１熱源側熱交換器３にも冷媒が流通するため、除霜が行われる。また、液配管４７に冷媒温度センサ１２が設けられている場合、制御装置３０にタイマ５３が設けられていなくてもよい。 In the configuration example shown in FIG. 1, the refrigerant temperature sensor 12 is provided in the second liquid pipe 44b, but the refrigerant temperature is in the liquid pipe 47 near the confluence of the first liquid pipe 44a and the second liquid pipe 44b. The sensor 12 may be provided. In this case, in step S104 shown in FIG. 5, the determination means 52 determines whether or not the temperature Tn2 of the refrigerant is equal to or higher than a predetermined temperature threshold value Ta. Then, as a result of the determination in step S104, when the temperature Tn2 of the refrigerant is equal to or higher than the temperature threshold Ta, the determination means 52 may transmit the switching instruction information to the second defrosting means 55. The temperature thresholds Ta and Tb have a relationship of, for example, Ta> Tb. Even if the refrigeration cycle device 1 proceeds to the process of step S105 before the defrosting of the first heat source side heat exchanger 3 is completely completed due to the relationship of Ta> Tb, the refrigerant also remains in the first heat source side heat exchanger 3. Defrosting is performed for distribution. Further, when the refrigerant temperature sensor 12 is provided in the liquid pipe 47, the timer 53 may not be provided in the control device 30.
　本実施の形態１の冷凍サイクル装置１は、圧縮機２と、膨張弁２２ａと、負荷側熱交換器２１ａと、流路切替装置５と、熱源側熱交換器１５と、開閉弁７と、制御装置３０とを有する。熱源側熱交換器１５は、流路切替装置５と膨張弁２２ａとの間に並列に接続される第１熱源側熱交換器３および第２熱源側熱交換器４を有する。開閉弁７は、除霜運転時に流通する冷媒の第２熱源側熱交換器４の下流側に設けられている。制御装置３０は、除霜運転を行う際、圧縮機２から吐出される冷媒が熱源側熱交換器１５に流入するように流路切替装置５を制御する。制御装置３０は、第１除霜手段５４と、判定手段５２と、第２除霜手段５５とを有する。第１除霜手段５４は、除霜運転が開始されるとき、開閉弁７を開状態から閉状態に切り替える。判定手段５２は、除霜対象の切り替えのタイミングを決定する。第２除霜手段は、判定手段５２によって決定されるタイミングにしたがって、開閉弁７を閉状態から開状態に切り替える。 The refrigeration cycle device 1 of the first embodiment includes a compressor 2, an expansion valve 22a, a load side heat exchanger 21a, a flow path switching device 5, a heat source side heat exchanger 15, an on-off valve 7, and the like. It has a control device 30 and. The heat source side heat exchanger 15 has a first heat source side heat exchanger 3 and a second heat source side heat exchanger 4 connected in parallel between the flow path switching device 5 and the expansion valve 22a. The on-off valve 7 is provided on the downstream side of the second heat source side heat exchanger 4 of the refrigerant that circulates during the defrosting operation. The control device 30 controls the flow path switching device 5 so that the refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 15 during the defrosting operation. The control device 30 includes a first defrosting means 54, a determining means 52, and a second defrosting means 55. The first defrosting means 54 switches the on-off valve 7 from the open state to the closed state when the defrosting operation is started. The determination means 52 determines the timing of switching the defrost target. The second defrosting means switches the on-off valve 7 from the closed state to the open state according to the timing determined by the determination means 52.
　本実施の形態１によれば、第１除霜手段５４は、除霜開始時に開閉弁７を閉じるので、圧縮機２から吐出された冷媒は、２つの熱源側熱交換器のうち、第１熱源側熱交換器３に集中的に流れる。その後、第２除霜手段５５が開閉弁７を開く。これにより、冷媒は、第２熱源側熱交換器４に流れるようになるが、第１熱源側熱交換器３にも流れる。２つの熱源側熱交換器に冷媒が流れる際、冷媒の熱の多くが第２熱源側熱交換器４で費やされるとともに、第１熱源側熱交換器３に残った霜が溶ける。そのため、直列に接続される２つの熱源側熱交換器を同時に除霜する場合よりも、冷媒の熱が無駄に消費されることが抑制される。その結果、２つの熱源側熱交換器を効率的に除霜することができる。 According to the first embodiment, the first defrosting means 54 closes the on-off valve 7 at the start of defrosting, so that the refrigerant discharged from the compressor 2 is the first of the two heat source side heat exchangers. It flows intensively to the heat exchanger 3 on the heat source side. After that, the second defrosting means 55 opens the on-off valve 7. As a result, the refrigerant flows to the second heat source side heat exchanger 4, but also flows to the first heat source side heat exchanger 3. When the refrigerant flows through the two heat source side heat exchangers, most of the heat of the refrigerant is consumed in the second heat source side heat exchanger 4, and the frost remaining in the first heat source side heat exchanger 3 melts. Therefore, wasteful consumption of the heat of the refrigerant is suppressed as compared with the case where two heat source side heat exchangers connected in series are defrosted at the same time. As a result, the two heat source side heat exchangers can be efficiently defrosted.
（変形例１）
　変形例１は、図１に示した冷凍サイクル装置１において、冷媒温度センサ１２が設けられていない場合である。変形例１においては、図１～図５を参照して説明した構成と同一の構成に同一の符号を付し、その詳細な説明を省略する。 (Modification example 1)
The first modification is the case where the refrigerating cycle device 1 shown in FIG. 1 is not provided with the refrigerant temperature sensor 12. In the first modification, the same components as those described with reference to FIGS. 1 to 5 are designated by the same reference numerals, and detailed description thereof will be omitted.
　変形例１の冷凍サイクル装置の構成を説明する。図６は、変形例１の冷凍サイクル装置の一構成例を示す冷媒回路図である。図７は、変形例１における制御装置の一構成例を示す機能ブロック図である。 The configuration of the refrigeration cycle device of the first modification will be described. FIG. 6 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the first modification. FIG. 7 is a functional block diagram showing a configuration example of the control device in the first modification.
　冷凍サイクル装置１ａの熱源側ユニット１０ａには、図１に示した冷媒温度センサ１２が設けられていない。判定手段５２は、切替指示情報を第２除霜手段５５に送信した後、タイマ５３が計測する時間ｔ１が予め決められた時間閾値ｔｔｈ２以上であるか否かを判定する。時間閾値ｔｔｈ１およびｔｔｈ２は、ｔｔｈ１＜ｔｔｈ２の関係である。判定手段５２は時間ｔ１が時間閾値ｔｔｈ２以上になると、除霜終了情報を冷凍サイクル制御手段５１に送信する。 The heat source side unit 10a of the refrigeration cycle device 1a is not provided with the refrigerant temperature sensor 12 shown in FIG. After transmitting the switching instruction information to the second defrosting means 55, the determining means 52 determines whether or not the time t1 measured by the timer 53 is equal to or greater than the predetermined time threshold tth2. The time thresholds tth1 and tth2 have a relationship of tth1 <tth2. When the time t1 becomes equal to or higher than the time threshold value tth2, the determination means 52 transmits the defrosting end information to the refrigeration cycle control means 51.
　変形例１の冷凍サイクル装置１ａの動作を、図５を参照して説明する。ここでは、図５に示した処理と異なる処理について説明し、図５を参照して説明した処理と同様な処理についての詳細な説明を省略する。 The operation of the refrigeration cycle device 1a of the first modification will be described with reference to FIG. Here, a process different from the process shown in FIG. 5 will be described, and detailed description of the process similar to the process described with reference to FIG. 5 will be omitted.
　ステップＳ１０６において、判定手段５２は、タイマ５３が計測する時間ｔ１が時間閾値ｔｔｈ２以上になったか否かを判定する。ステップＳ１０６の判定の結果、判定手段５２は、時間ｔ１が時間閾値ｔｔｈ２以上になると、除霜終了情報を冷凍サイクル制御手段５１に送信する。 In step S106, the determination means 52 determines whether or not the time t1 measured by the timer 53 is equal to or greater than the time threshold value tth2. As a result of the determination in step S106, when the time t1 becomes the time threshold value tth2 or more, the determination means 52 transmits the defrosting end information to the refrigeration cycle control means 51.
　変形例１によれば、冷媒温度センサ１２が設けられていなくても、本実施の形態１の効果が得られる。 According to the first modification, the effect of the first embodiment can be obtained even if the refrigerant temperature sensor 12 is not provided.
（変形例２）
　変形例２は、図１に示した冷凍サイクル装置１において、流量調整弁および冷媒温度センサが第１液配管４４ａに設けられている場合である。変形例２においては、図１～図７を参照して説明した構成と同一の構成に同一の符号を付し、その詳細な説明を省略する。 (Modification 2)
The second modification is the case where the flow rate adjusting valve and the refrigerant temperature sensor are provided in the first liquid pipe 44a in the refrigerating cycle device 1 shown in FIG. In the second modification, the same components as those described with reference to FIGS. 1 to 7 are designated by the same reference numerals, and detailed description thereof will be omitted.
　変形例２の冷凍サイクル装置の構成を説明する。図８は、変形例２の冷凍サイクル装置の一構成例を示す冷媒回路図である。図９は、変形例２における制御装置の一構成例を示す機能ブロック図である。図８に示すように、冷凍サイクル装置１ｂの熱源側ユニット１０ｂの第１液配管４４ａには、冷媒温度センサ１２ａおよび流量調整弁９が設けられている。冷媒温度センサ１２ａは、第１液配管４４ａを流通する冷媒の温度Ｔｎ１を検出する。流量調整弁９は、閉状態および開状態のうち、一方の状態から他方の状態に切り替えることができる。また、流量調整弁９は、開度を変化させることで、流通する冷媒の流量を調整することができる。図９に示すように、変形例２の制御装置３０は図２に示したタイマ５３を有していない。制御装置３０は、冷媒の温度Ｔｎ１について、除霜対象の切り替えのタイミングを決める判定基準になる値として温度閾値Ｔａを予め記憶している。ＴａおよびＴｂは同じ値でもよく、異なる値でもよい。 The configuration of the refrigeration cycle device of the second modification will be described. FIG. 8 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the second modification. FIG. 9 is a functional block diagram showing a configuration example of the control device in the second modification. As shown in FIG. 8, a refrigerant temperature sensor 12a and a flow rate adjusting valve 9 are provided in the first liquid pipe 44a of the heat source side unit 10b of the refrigeration cycle device 1b. The refrigerant temperature sensor 12a detects the temperature Tn1 of the refrigerant flowing through the first liquid pipe 44a. The flow rate adjusting valve 9 can switch from one of the closed state and the open state to the other state. Further, the flow rate adjusting valve 9 can adjust the flow rate of the flowing refrigerant by changing the opening degree. As shown in FIG. 9, the control device 30 of the second modification does not have the timer 53 shown in FIG. The control device 30 stores in advance the temperature threshold value Ta as a value that serves as a determination standard for determining the timing of switching the defrosting target for the refrigerant temperature Tn1. Ta and Tb may have the same value or different values.
　次に、変形例２の冷凍サイクル装置１ｂの動作を説明する。図１０は、図８に示した冷凍サイクル装置の動作手順の一例を示すフローチャートである。冷凍サイクル装置１ｂは図１０に示す動作手順を開始する前、暖房運転を行っており、流量調整弁９および開閉弁７は開状態であるものとする。図１０に示すステップＳ２０１およびＳ２０２の処理は、図５を参照して説明したステップＳ１０１およびＳ１０２の処理と同様なため、その詳細な説明を省略する。 Next, the operation of the refrigeration cycle device 1b of the modification 2 will be described. FIG. 10 is a flowchart showing an example of the operation procedure of the refrigeration cycle apparatus shown in FIG. It is assumed that the refrigerating cycle device 1b is in the heating operation before starting the operation procedure shown in FIG. 10, and the flow rate adjusting valve 9 and the on-off valve 7 are in the open state. Since the processes of steps S201 and S202 shown in FIG. 10 are the same as the processes of steps S101 and S102 described with reference to FIG. 5, detailed description thereof will be omitted.
　ステップＳ２０１の判定の後、判定手段５２は、冷凍サイクル制御手段５１から除霜開始情報を受信すると、除霜開始情報を第１除霜手段５４に転送するとともに、冷媒温度センサ１２ａによって検出される冷媒の温度Ｔｎ１を監視する。第１除霜手段５４は、除霜開始情報を判定手段５２から受信すると、開閉弁７を閉じる（ステップＳ２０３）。判定手段５２は、冷媒の温度Ｔｎ１が温度閾値Ｔａ以上になったか否かを判定する（ステップＳ２０４）。判定手段５２は、ステップＳ２０４において、冷媒の温度Ｔｎ１が温度閾値Ｔａ以上になると、切替指示情報を第２除霜手段５５に送信する。 After the determination in step S201, when the determination means 52 receives the defrosting start information from the refrigeration cycle control means 51, the determination means 52 transfers the defrosting start information to the first defrosting means 54 and is detected by the refrigerant temperature sensor 12a. The temperature Tn1 of the refrigerant is monitored. When the first defrosting means 54 receives the defrosting start information from the determining means 52, the first defrosting means 54 closes the on-off valve 7 (step S203). The determination means 52 determines whether or not the temperature Tn1 of the refrigerant is equal to or higher than the temperature threshold value Ta (step S204). In step S204, when the temperature Tn1 of the refrigerant becomes equal to or higher than the temperature threshold value Ta, the determination means 52 transmits the switching instruction information to the second defrosting means 55.
　第２除霜手段５５は、切替指示情報を判定手段５２から受信すると、開閉弁７を開き（ステップＳ２０５）、流量調整弁９を閉じる（ステップＳ２０６）。判定手段５２は、切替指示情報を第２除霜手段５５に送信した後、冷媒温度センサ１２ｂによって検出される冷媒の温度Ｔｎ２が温度閾値Ｔｂ以上になったか否かを判定する（ステップＳ２０７）。判定手段５２は、冷媒の温度Ｔｎ２が温度閾値Ｔｂ以上になると、熱源側熱交換器１５の除霜が終了したと判定し、除霜終了情報を第２除霜手段５５および冷凍サイクル制御手段５１に送信する。 When the second defrosting means 55 receives the switching instruction information from the determining means 52, the on-off valve 7 is opened (step S205) and the flow rate adjusting valve 9 is closed (step S206). After transmitting the switching instruction information to the second defrosting means 55, the determining means 52 determines whether or not the temperature Tn2 of the refrigerant detected by the refrigerant temperature sensor 12b is equal to or higher than the temperature threshold value Tb (step S207). When the temperature Tn2 of the refrigerant becomes equal to or higher than the temperature threshold value Tb, the determination means 52 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and sends the defrosting end information to the second defrosting means 55 and the refrigeration cycle control means 51. Send to.
　第２除霜手段５５は、除霜終了情報を判定手段５２から受信すると、流量調整弁９を開く（ステップＳ２０８）。冷凍サイクル制御手段５１は、除霜終了情報を判定手段５２から受信すると、流路切替装置５を制御して流路を切り替える（ステップＳ２０９）。これにより、圧縮機２から吐出される冷媒は、流路切替装置５を経由して負荷側ユニット２０ａおよび２０ｂに流入する。冷凍サイクル装置１の運転モードが除霜運転から暖房運転に戻る。 When the second defrosting means 55 receives the defrosting end information from the determination means 52, the second defrosting means 55 opens the flow rate adjusting valve 9 (step S208). When the refrigeration cycle control means 51 receives the defrosting end information from the determination means 52, the refrigeration cycle control means 51 controls the flow path switching device 5 to switch the flow path (step S209). As a result, the refrigerant discharged from the compressor 2 flows into the load- side units 20a and 20b via the flow path switching device 5. The operation mode of the refrigeration cycle device 1 returns from the defrosting operation to the heating operation.
　なお、図１０に示したステップＳ２０６において、第２除霜手段５５は、流量調整弁９を閉じているが、流量調整弁９を完全に閉めないで、流量調整弁９の開度を小さくして冷媒を少し流通させてもよい。この場合、ステップＳ２０８において、第２除霜手段５５は、流量調整弁９を全開にする。 In step S206 shown in FIG. 10, the second defrosting means 55 closes the flow rate adjusting valve 9, but does not completely close the flow rate adjusting valve 9 and reduces the opening degree of the flow rate adjusting valve 9. The refrigerant may be circulated a little. In this case, in step S208, the second defrosting means 55 fully opens the flow rate adjusting valve 9.
　変形例２によれば、並列に接続される第１熱源側熱交換器３および第２熱源側熱交換器４のそれぞれの液配管に冷媒の流通を遮断する弁が設けられている。変形例２の冷凍サイクル装置１ｂが、除霜運転の際、各弁の開閉を制御して、はじめに第１熱源側熱交換器３を集中的に除霜した後、残りの第２熱源側熱交換器４を集中的に除霜することで、確実、かつ効率よく除霜を行うことができる。 According to the second modification, a valve for shutting off the flow of the refrigerant is provided in each of the liquid pipes of the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 connected in parallel. The refrigeration cycle device 1b of the second modification controls the opening and closing of each valve during the defrosting operation to first intensively defrost the first heat source side heat exchanger 3, and then the remaining second heat source side heat. By intensively defrosting the exchanger 4, defrosting can be performed reliably and efficiently.
　また、判定手段５２は、主な除霜対象が第１熱源側熱交換器３から第２熱源側熱交換器４に切り替えるタイミングを冷媒の温度Ｔｎ１によって判定している。そのため、判定手段５２は、タイマ５３によって計測される時間ｔ１よりも、第１熱源側熱交換器３に霜が残っているか否かの状態をより正確に判定できる。また、変形例２によれば、制御装置３０にタイマ５３が設けられていなくてもよい。 Further, the determination means 52 determines the timing at which the main defrost target is switched from the first heat source side heat exchanger 3 to the second heat source side heat exchanger 4 based on the temperature Tn1 of the refrigerant. Therefore, the determination means 52 can more accurately determine the state of whether or not frost remains in the first heat source side heat exchanger 3 than the time t1 measured by the timer 53. Further, according to the second modification, the timer 53 may not be provided in the control device 30.
（変形例３）
　変形例３は、図１に示した冷凍サイクル装置１において、３つ以上の熱源側熱交換器が並列に接続される場合である。変形例３においては、図１～図１０を参照して説明した構成と同一の構成に同一の符号を付し、その詳細な説明を省略する。 (Modification example 3)
A modification 3 is a case where three or more heat source side heat exchangers are connected in parallel in the refrigeration cycle apparatus 1 shown in FIG. In the third modification, the same components as those described with reference to FIGS. 1 to 10 are designated by the same reference numerals, and detailed description thereof will be omitted.
　変形例２の冷凍サイクル装置の構成を説明する。図１１は、変形例３の冷凍サイクル装置の一構成例を示す冷媒回路図である。図１１に示すように、冷凍サイクル装置１ｃの熱源側ユニット１０ｃにおいて、第１熱源側熱交換器３および第２熱源側熱交換器４と並列に接続される第３熱源側熱交換器８が設けられている。第３熱源側熱交換器８は、第３ガス配管４３ｃを介してガス配管４１と接続され、第３液配管４４ｃを介して液配管４７と接続されている。 The configuration of the refrigeration cycle device of the second modification will be described. FIG. 11 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the modified example 3. As shown in FIG. 11, in the heat source side unit 10c of the refrigeration cycle apparatus 1c, the third heat source side heat exchanger 8 connected in parallel with the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4 It is provided. The third heat source side heat exchanger 8 is connected to the gas pipe 41 via the third gas pipe 43c, and is connected to the liquid pipe 47 via the third liquid pipe 44c.
　第３液配管４４ｃには、冷媒温度センサ１２ｃおよび第２流量調整弁９ｂが設けられている。冷媒温度センサ１２ｃは、第３液配管４４ｃを流通する冷媒の温度Ｔｎ３を検出する。判定手段５２は、冷媒の温度Ｔｎ３と予め決められた温度閾値Ｔｄと比較し、冷媒の温度Ｔｎ３が温度閾値Ｔｄ以上になると、除霜対象を切り替える。なお、第１流量調整弁９ａおよび第２流量調整弁９ｂは流量調整弁９と同様な構成であり、冷媒温度センサ１２ｃは冷媒温度センサ１２と同様な構成であるため、これらの詳細な説明を省略する。 The third liquid pipe 44c is provided with a refrigerant temperature sensor 12c and a second flow rate adjusting valve 9b. The refrigerant temperature sensor 12c detects the temperature Tn3 of the refrigerant flowing through the third liquid pipe 44c. The determination means 52 compares the temperature Tn3 of the refrigerant with the predetermined temperature threshold Td, and when the temperature Tn3 of the refrigerant becomes equal to or higher than the temperature threshold Td, the defrosting target is switched. The first flow rate adjusting valve 9a and the second flow rate adjusting valve 9b have the same configuration as the flow rate adjusting valve 9, and the refrigerant temperature sensor 12c has the same configuration as the refrigerant temperature sensor 12. Omit.
　変形例２の冷凍サイクル装置１ｃの動作を、図１０を参照して説明する。ここでは、図１０に示した処理と異なる処理について説明し、図１０を参照して説明した処理と同様な処理についての詳細な説明を省略する。初期状態として、開閉弁７、第１流量調整弁９ａおよび第２流量調整弁９ｂは開状態である。 The operation of the refrigeration cycle device 1c of the second modification will be described with reference to FIG. Here, a process different from the process shown in FIG. 10 will be described, and detailed description of the process similar to the process described with reference to FIG. 10 will be omitted. As an initial state, the on-off valve 7, the first flow rate adjusting valve 9a, and the second flow rate adjusting valve 9b are in the open state.
　ステップＳ２０３において、第１除霜手段５４は、除霜開始情報を判定手段５２から受信すると、第１流量調整弁９ａの開状態を維持し、開閉弁７および第２流量調整弁９ｂを閉じる。ステップＳ２０６において、第２除霜手段５５は、第１流量調整弁９ａを閉じる。ステップＳ２０７において、判定手段５２は、冷媒の温度Ｔｎ２が温度閾値Ｔｂ以上になると、切替指示情報を第２除霜手段５５に送信する。第２除霜手段５５は、ステップＳ２０６の後、切替指示情報を判定手段５２から受信すると、開閉弁７を閉じ、第２流量調整弁９ｂを開く。 In step S203, when the first defrosting means 54 receives the defrosting start information from the determining means 52, the first flow rate adjusting valve 9a is maintained in the open state, and the on-off valve 7 and the second flow rate adjusting valve 9b are closed. In step S206, the second defrosting means 55 closes the first flow rate adjusting valve 9a. In step S207, when the temperature Tn2 of the refrigerant becomes equal to or higher than the temperature threshold value Tb, the determination means 52 transmits the switching instruction information to the second defrosting means 55. After step S206, when the second defrosting means 55 receives the switching instruction information from the determining means 52, the second defrosting means 55 closes the on-off valve 7 and opens the second flow rate adjusting valve 9b.
　判定手段５２は、ステップＳ２０７の判定結果により切替指示情報を第２除霜手段５５に送信した後、冷媒温度センサ１２ｃによって検出される冷媒の温度Ｔｎ３が温度閾値Ｔｄ以上になったか否かを判定する。判定手段５２は、冷媒の温度Ｔｎ３が温度閾値Ｔｄ以上になると、熱源側熱交換器１５の除霜が終了したと判定し、除霜終了情報を第２除霜手段５５および冷凍サイクル制御手段５１に送信する。その後、制御装置３０は、ステップＳ２０８およびＳ２０９の処理を行う。 The determination means 52 determines whether or not the temperature Tn3 of the refrigerant detected by the refrigerant temperature sensor 12c is equal to or higher than the temperature threshold value Td after transmitting the switching instruction information to the second defrosting means 55 based on the determination result in step S207. To do. When the temperature Tn3 of the refrigerant becomes equal to or higher than the temperature threshold value Td, the determination means 52 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and sends the defrosting end information to the second defrosting means 55 and the refrigeration cycle control means 51. Send to. After that, the control device 30 performs the processes of steps S208 and S209.
　なお、図１１は、３つの熱源側熱交換器が並列に接続される場合を示しているが、並列接続される熱源側熱交換器は４つ以上であってもよい。この場合、各熱源側熱交換器の液配管側に、流量調整装置および冷媒温度センサが設けられている。また、図１１に示す冷凍サイクル装置１ｃにおいて、判定手段５２は、除霜対象の切り替えのタイミングを、図２に示したタイマ５３によって計測される時間ｔ１に基づいて判定してもよい。この場合、冷媒温度センサ１２ａ～１２ｃが設けられていなくてもよい。 Although FIG. 11 shows a case where three heat source side heat exchangers are connected in parallel, the number of heat source side heat exchangers connected in parallel may be four or more. In this case, a flow rate adjusting device and a refrigerant temperature sensor are provided on the liquid piping side of each heat source side heat exchanger. Further, in the refrigeration cycle device 1c shown in FIG. 11, the determination means 52 may determine the timing of switching the defrosting target based on the time t1 measured by the timer 53 shown in FIG. In this case, the refrigerant temperature sensors 12a to 12c may not be provided.
　変形例３によれば、並列に接続される熱源側熱交換器の数が３つ以上であっても、効率よく除霜することができる。 According to Modification 3, even if the number of heat source side heat exchangers connected in parallel is three or more, defrosting can be performed efficiently.
実施の形態２．
　本実施の形態２の冷凍サイクル装置は、流通する冷媒を分流および合流するヘッダが熱源側熱交換器に設けられた場合である。実施の形態２においては、実施の形態１において説明した構成と同一の構成に同一の符号を付し、その詳細な説明を省略する。 Embodiment 2.
The refrigeration cycle apparatus of the second embodiment is a case where a header for dividing and merging the flowing refrigerant is provided in the heat source side heat exchanger. In the second embodiment, the same components as those described in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted.
　本実施の形態２の冷凍サイクル装置の構成を説明する。図１２は、実施の形態２に係る冷凍サイクル装置の一構成例を示す冷媒回路図である。冷凍サイクル装置１ｄは、熱源側ユニット１０ｄを有する。熱源側ユニット１０ｄにおいて、第１熱源側熱交換器３の第１ガス配管４３ａ側に第１ガスヘッダ６１が設けられ、第１熱源側熱交換器３の第１液配管４４ａ側に第１液ヘッダ６２が設けられている。また、熱源側ユニット１０ｄにおいて、第２熱源側熱交換器４の第２ガス配管４３ｂ側に第２ガスヘッダ６３が設けられ、第２熱源側熱交換器４の第２液配管４４ｂ側に第２液ヘッダ６４が設けられている。 The configuration of the refrigeration cycle device of the second embodiment will be described. FIG. 12 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device according to the second embodiment. The refrigeration cycle device 1d has a heat source side unit 10d. In the heat source side unit 10d, the first gas header 61 is provided on the first gas pipe 43a side of the first heat source side heat exchanger 3, and the first liquid header 61 is provided on the first liquid pipe 44a side of the first heat source side heat exchanger 3. 62 is provided. Further, in the heat source side unit 10d, the second gas header 63 is provided on the second gas pipe 43b side of the second heat source side heat exchanger 4, and the second gas header 63 is provided on the second liquid pipe 44b side of the second heat source side heat exchanger 4. A liquid header 64 is provided.
　図１３は、図１２に示した第１熱源側熱交換器の一構成例を示す側面図である。図１４は、図１２に示した第２熱源側熱交換器の一構成例を示す側面図である。図１３および図１４において、説明の便宜上、方向を定義するためにＸ軸およびＺ軸を図に示している。図１３および図１４に示すＺ軸矢印の反対方向が重力方向である。図１３および図１４に示す実線矢印は、冷凍サイクル装置１が冷房運転および除霜運転を行うときの冷媒の流通方向を示す。図１３および図１４に示す破線矢印は、冷凍サイクル装置１が暖房運転を行うときの冷媒の流通方向を示す。 FIG. 13 is a side view showing a configuration example of the first heat source side heat exchanger shown in FIG. FIG. 14 is a side view showing a configuration example of the second heat source side heat exchanger shown in FIG. In FIGS. 13 and 14, for convenience of explanation, the X-axis and the Z-axis are shown in the figure to define the direction. The direction opposite to the Z-axis arrow shown in FIGS. 13 and 14 is the direction of gravity. The solid arrows shown in FIGS. 13 and 14 indicate the flow direction of the refrigerant when the refrigerating cycle device 1 performs the cooling operation and the defrosting operation. The broken line arrows shown in FIGS. 13 and 14 indicate the flow direction of the refrigerant when the refrigeration cycle device 1 performs the heating operation.
　図１３に示すように、第１熱源側熱交換器３は、複数の伝熱管４５ａと、複数の放熱フィン４６ａとを有する。第１ガスヘッダ６１に第１ガス配管４３ａが接続されている。第１ガス配管４３ａが第１ガスヘッダ６１に接続される位置は、第１ガスヘッダ６１の地面に対して垂直方向（Ｚ軸矢印方向）の長さである高さの中央部である。中央部は、第１ガスヘッダ６１の高さの正確な中心の位置に限らず、中心の位置を基準とした一定の範囲の高さを含む。第１液ヘッダ６２の下部に第１液配管４４ａが接続されている。第１ガスヘッダ６１は、冷凍サイクル装置１が冷房運転および除霜運転を行う際、第１ガス配管４３ａから流入する冷媒を複数の伝熱管４５ａに分流する。第１ガスヘッダ６１は、冷凍サイクル装置１が暖房運転を行う際、複数の伝熱管４５ａから流入する冷媒を合流して第１ガス配管４３ａに流出する。 As shown in FIG. 13, the first heat source side heat exchanger 3 has a plurality of heat transfer tubes 45a and a plurality of heat radiation fins 46a. The first gas pipe 43a is connected to the first gas header 61. The position where the first gas pipe 43a is connected to the first gas header 61 is the central portion of the height which is the length of the first gas header 61 in the direction perpendicular to the ground (Z-axis arrow direction). The central portion includes not only the exact center position of the height of the first gas header 61 but also a height in a certain range with respect to the center position. The first liquid pipe 44a is connected to the lower part of the first liquid header 62. The first gas header 61 divides the refrigerant flowing from the first gas pipe 43a into the plurality of heat transfer pipes 45a when the refrigerating cycle device 1 performs the cooling operation and the defrosting operation. When the refrigeration cycle device 1 performs the heating operation, the first gas header 61 merges the refrigerants flowing in from the plurality of heat transfer pipes 45a and flows out to the first gas pipe 43a.
　図１４に示すように、第２熱源側熱交換器４は、複数の伝熱管４５ｂと、複数の放熱フィン４６ｂとを有する。第２ガスヘッダ６３に第２ガス配管４３ｂが接続されている。第２ガス配管４３ｂが第２ガスヘッダ６３に接続される位置は、第２ガスヘッダ６３の地面に対して垂直方向（Ｚ軸矢印方向）の長さである高さの中央部である。中央部は、第２ガスヘッダ６３の高さの正確な中心の位置に限らず、中心の位置を基準とした一定の範囲の高さを含む。第２液ヘッダ６４の下部に第２液配管４４ｂが接続されている。第２ガスヘッダ６３は、冷凍サイクル装置１が冷房運転および除霜運転を行う際、第２ガス配管４３ｂから流入する冷媒を複数の伝熱管４５ｂに分流する。第２ガスヘッダ６３は、冷凍サイクル装置１が暖房運転を行う際、複数の伝熱管４５ｂから流入する冷媒を合流して第２ガス配管４３ｂに流出する。 As shown in FIG. 14, the second heat source side heat exchanger 4 has a plurality of heat transfer tubes 45b and a plurality of heat radiation fins 46b. The second gas pipe 43b is connected to the second gas header 63. The position where the second gas pipe 43b is connected to the second gas header 63 is the central portion of the height which is the length of the second gas header 63 in the direction perpendicular to the ground (Z-axis arrow direction). The central portion includes not only the exact center position of the height of the second gas header 63 but also a certain range of heights based on the center position. The second liquid pipe 44b is connected to the lower part of the second liquid header 64. The second gas header 63 divides the refrigerant flowing from the second gas pipe 43b into the plurality of heat transfer pipes 45b when the refrigerating cycle device 1 performs the cooling operation and the defrosting operation. When the refrigeration cycle device 1 performs the heating operation, the second gas header 63 merges the refrigerants flowing in from the plurality of heat transfer pipes 45b and flows out to the second gas pipe 43b.
　本実施の形態２においては、第１熱源側熱交換器３の高さと第２熱源側熱交換器４の高さとが同等であり、伝熱管４５ａの本数と伝熱管４５ｂの本数とが同じ場合である。図１３および図１４において、伝熱管４５ａの本数および伝熱管４５ｂの本数が１３本の場合を示しているが、伝熱管４５ａおよび４５ｂの本数は１３本の場合に限らない。 In the second embodiment, the height of the first heat source side heat exchanger 3 and the height of the second heat source side heat exchanger 4 are the same, and the number of heat transfer tubes 45a and the number of heat transfer tubes 45b are the same. Is. 13 and 14 show the case where the number of heat transfer tubes 45a and the number of heat transfer tubes 45b is 13, but the number of heat transfer tubes 45a and 45b is not limited to 13.
　なお、本実施の形態２の冷凍サイクル装置１ｄの動作は、図５を参照して説明した動作手順と同様になるため、その詳細な説明を省略する。 Since the operation of the refrigeration cycle device 1d according to the second embodiment is the same as the operation procedure described with reference to FIG. 5, detailed description thereof will be omitted.
　本実施の形態２の冷凍サイクル装置１ｄによる作用および効果をわかりやすく説明するために、比較例の冷凍サイクル装置の構成を説明する。図１５は、比較例の冷凍サイクル装置の構成例を示す冷媒回路図である。図１および図１２を参照して説明した構成と同一の構成については同一の符号を付し、その詳細な説明を省略する。 In order to explain the action and effect of the refrigeration cycle device 1d of the second embodiment in an easy-to-understand manner, the configuration of the refrigeration cycle device of the comparative example will be described. FIG. 15 is a refrigerant circuit diagram showing a configuration example of a refrigeration cycle device of a comparative example. The same components as those described with reference to FIGS. 1 and 12 are designated by the same reference numerals, and detailed description thereof will be omitted.
　図１５に示すように、比較例の冷凍サイクル装置１００は、熱源側ユニット１１０と、負荷側ユニット２０ａおよび２０ｂと、制御装置１３０とを有する。除霜運転時に冷媒が流通する方向を基準として、第１液配管４４ａおよび第２液配管４４ｂが合流する位置よりも下流側の液配管４７に冷媒温度センサ１２１が設けられている。冷媒温度センサ１２１は、液配管４７を流通する冷媒の温度Ｔｒを検出し、冷媒の温度Ｔｒの情報を制御装置１３０に送信する。制御装置１３０のハードウェア構成は図３および図４を参照して説明した構成と同様なため、その詳細な説明を省略する。 As shown in FIG. 15, the refrigeration cycle device 100 of the comparative example has a heat source side unit 110, load side units 20a and 20b, and a control device 130. A refrigerant temperature sensor 121 is provided in the liquid pipe 47 on the downstream side of the position where the first liquid pipe 44a and the second liquid pipe 44b meet, with reference to the direction in which the refrigerant flows during the defrosting operation. The refrigerant temperature sensor 121 detects the temperature Tr of the refrigerant flowing through the liquid pipe 47, and transmits information on the temperature Tr of the refrigerant to the control device 130. Since the hardware configuration of the control device 130 is the same as the configuration described with reference to FIGS. 3 and 4, detailed description thereof will be omitted.
　図１２に示した構成と比較すると、図１５に示す熱源側ユニット１１０の第２液配管４４ｂには、図１に示した開閉弁７が設けられていない。冷凍サイクル装置１００が除霜運転を行う場合、制御装置１３０は、冷媒の温度Ｔｒと予め決められた温度閾値Ｔｃとを比較する。そして、制御装置１３０は、冷媒の温度Ｔｒが温度閾値Ｔｃ以上になると、除霜が終了したと判定する。温度閾値Ｔｃは、例えば、１０℃である。温度閾値ＴｂおよびＴｃは、Ｔｃ＞Ｔｂの関係である。また、温度閾値をＴｃは、変形例２で述べた温度閾値Ｔａと比較すると、Ｔａ＜Ｔｃの関係である。 Compared with the configuration shown in FIG. 12, the second liquid pipe 44b of the heat source side unit 110 shown in FIG. 15 is not provided with the on-off valve 7 shown in FIG. When the refrigeration cycle device 100 performs the defrosting operation, the control device 130 compares the temperature Tr of the refrigerant with the predetermined temperature threshold Tc. Then, the control device 130 determines that the defrosting is completed when the temperature Tr of the refrigerant becomes equal to or higher than the temperature threshold value Tc. The temperature threshold Tc is, for example, 10 ° C. The temperature thresholds Tb and Tc have a relationship of Tc> Tb. Further, when the temperature threshold value Tc is compared with the temperature threshold value Ta described in the second modification, the relationship is Ta <Tc.
　次に、図１５に示した比較例の冷凍サイクル装置１００の動作を、図１６を参照して説明する。図１６は、図１５に示した比較例の冷凍サイクル装置の動作手順の一例を示すフローチャートである。冷凍サイクル装置１００は、図１６に示す動作手順を開始する前、暖房運転を行っているものとする。 Next, the operation of the refrigeration cycle device 100 of the comparative example shown in FIG. 15 will be described with reference to FIG. FIG. 16 is a flowchart showing an example of the operation procedure of the refrigeration cycle device of the comparative example shown in FIG. It is assumed that the refrigeration cycle device 100 is in the heating operation before starting the operation procedure shown in FIG.
　制御装置１３０は、冷媒の温度Ｔｅが温度閾値Ｔ０以上になったか否かを判定する（ステップＳ１００１）。制御装置１３０は、ステップＳ１００１において、冷媒の温度Ｔｅが温度閾値Ｔ０以下になると、熱源側熱交換器１５に霜が付着したと判定し、流路切替装置５を制御して流路を切り替える（ステップＳ１００２）。これにより、圧縮機２から吐出される冷媒は、流路切替装置５を経由して熱源側熱交換器１５に流入する。 The control device 130 determines whether or not the temperature Te of the refrigerant is equal to or higher than the temperature threshold value T0 (step S1001). In step S1001, the control device 130 determines that frost has adhered to the heat source side heat exchanger 15 when the temperature Te of the refrigerant becomes equal to or lower than the temperature threshold value T0, and controls the flow path switching device 5 to switch the flow path ( Step S1002). As a result, the refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 15 via the flow path switching device 5.
　続いて、制御装置１３０は、冷媒の温度Ｔｒが温度閾値Ｔｃ以上であるか否かを判定する（ステップＳ１００３）。制御装置１３０は、ステップＳ１００３において、冷媒の温度Ｔｒが温度閾値Ｔｃ以上になると、熱源側熱交換器１５の除霜が終了したと判定し、流路切替装置５を制御して流路を切り替える（ステップＳ１００４）。冷凍サイクル装置１００の運転モードが除霜運転から暖房運転に戻る。 Subsequently, the control device 130 determines whether or not the temperature Tr of the refrigerant is equal to or higher than the temperature threshold value Tc (step S1003). In step S1003, when the temperature Tr of the refrigerant becomes equal to or higher than the temperature threshold value Tc, the control device 130 determines that the defrosting of the heat source side heat exchanger 15 has been completed, and controls the flow path switching device 5 to switch the flow path. (Step S1004). The operation mode of the refrigeration cycle device 100 returns from the defrosting operation to the heating operation.
　冷凍サイクル装置１００の除霜運転中、図１３に示した第１熱源側熱交換器３において、第１ガスヘッダ６１の中央部に第１ガス配管４３ａからガス冷媒が流入する。第１ガスヘッダ６１に流入したガス冷媒は複数の伝熱管４５ａに分流するが、圧力損失によって、第１熱源側熱交換器３の下段側の伝熱管４５ａに冷媒が滞留しやすくなる。図１４示した第２熱源側熱交換器４についても、第１熱源側熱交換器３と同様に、除霜運転の際、第２熱源側熱交換器４の下段側の伝熱管４５ｂに冷媒が滞留しやすくなる。 During the defrosting operation of the refrigeration cycle device 100, in the first heat source side heat exchanger 3 shown in FIG. 13, the gas refrigerant flows into the central portion of the first gas header 61 from the first gas pipe 43a. The gas refrigerant that has flowed into the first gas header 61 is diverted to the plurality of heat transfer tubes 45a, but due to the pressure loss, the refrigerant tends to stay in the heat transfer tubes 45a on the lower stage side of the first heat source side heat exchanger 3. Similarly to the first heat source side heat exchanger 3, the second heat source side heat exchanger 4 shown in FIG. 14 also has a refrigerant in the heat transfer tube 45b on the lower stage side of the second heat source side heat exchanger 4 during the defrosting operation. Is likely to stay.
　図１７は、除霜運転時において、冷媒流量と熱源側熱交換器の位置との関係の一例を示すグラフである。図１７の横軸は冷媒の流量を示し、縦軸は図１３に示した第１熱源側熱交換器３の垂直方向（Ｚ軸矢印方向）における伝熱管４５ａの高さＨｕを示す。図１７の縦軸において、第１熱源側熱交換器３の複数の伝熱管４５ａのうち、最下段の伝熱管４５ａの高さをＨｕ１とし、最上段の伝熱管４５ａの高さをＨｕｎとしている。また、図１７において、実線のグラフは本実施の形態２の冷凍サイクル装置１ｄの場合であり、破線のグラフは図１５に示した比較例の冷凍サイクル装置１００の場合である。さらに、第２熱源側熱交換器４についても、図１７に示したグラフと同様な傾向になるため、ここでは、第２熱源側熱交換器４の場合の説明を省略する。 FIG. 17 is a graph showing an example of the relationship between the flow rate of the refrigerant and the position of the heat exchanger on the heat source side during the defrosting operation. The horizontal axis of FIG. 17 shows the flow rate of the refrigerant, and the vertical axis shows the height Hu of the heat transfer tube 45a in the vertical direction (Z-axis arrow direction) of the first heat source side heat exchanger 3 shown in FIG. In the vertical axis of FIG. 17, among the plurality of heat transfer tubes 45a of the first heat source side heat exchanger 3, the height of the lowermost heat transfer tube 45a is Hu1, and the height of the uppermost heat transfer tube 45a is Hun. .. Further, in FIG. 17, the solid line graph is the case of the refrigeration cycle device 1d of the second embodiment, and the broken line graph is the case of the refrigeration cycle device 100 of the comparative example shown in FIG. Further, since the second heat source side heat exchanger 4 has the same tendency as the graph shown in FIG. 17, the description of the second heat source side heat exchanger 4 will be omitted here.
　比較例の冷凍サイクル装置１００の除霜運転の際、冷媒が第１熱源側熱交換器および第２熱源側熱交換器に分流すると、図１７の破線のグラフに示すように、熱源側熱交換器１５における上段側に比べて下段側の冷媒の流量が小さくなっている。これは、図１３および図１４を参照して説明したように、ヘッダの中央部から複数の伝熱管に冷媒が分流する場合、圧力損失が原因で冷媒の流れがわるくなり、下段側で冷媒が滞留しやすくなるためである。 When the refrigerant is diverted to the first heat source side heat exchanger and the second heat source side heat exchanger during the defrosting operation of the refrigeration cycle device 100 of the comparative example, the heat exchange on the heat source side is shown as shown in the graph of the broken line in FIG. The flow rate of the refrigerant on the lower stage side is smaller than that on the upper stage side in the vessel 15. This is because, as described with reference to FIGS. 13 and 14, when the refrigerant flows from the central portion of the header to the plurality of heat transfer tubes, the flow of the refrigerant becomes stagnant due to the pressure loss, and the refrigerant flows on the lower side. This is because it tends to stay.
　そのため、比較例の冷凍サイクル装置１００においては、熱源側熱交換器１５の下段側の伝熱管に流れる冷媒の流量を考慮して、熱源側熱交換器１５の除霜を終了するまで長い時間を必要とし、温度閾値Ｔｃが高い値に設定される。その結果、図１７の破線のグラフに示すように、熱源側熱交換器１５の下段側の伝熱管の除霜が終了するまで、上段側において冷媒が無駄に流れてしまうことになる。 Therefore, in the refrigeration cycle device 100 of the comparative example, it takes a long time to complete the defrosting of the heat source side heat exchanger 15 in consideration of the flow rate of the refrigerant flowing through the lower heat transfer tube of the heat source side heat exchanger 15. It is required and the temperature threshold Tc is set to a high value. As a result, as shown in the broken line graph of FIG. 17, the refrigerant flows wastefully on the upper side until the defrosting of the heat transfer tube on the lower side of the heat source side heat exchanger 15 is completed.
　これに対して、本実施の形態２の冷凍サイクル装置１ｄは、図１７の実線のグラフに示すように、冷媒流量は第１熱源側熱交換器３における伝熱管４５ａの高さの違いに対する影響が比較例に比べて小さく、複数の伝熱管４５ａにより均等に冷媒が流通する。そのため、温度閾値Ｔｂを温度閾値Ｔｃよりも低い温度に設定することができ、比較例に比べて、効率よく除霜を行うことができる。 On the other hand, in the refrigeration cycle device 1d of the second embodiment, as shown in the solid line graph of FIG. 17, the refrigerant flow rate has an influence on the difference in the height of the heat transfer tube 45a in the first heat source side heat exchanger 3. Is smaller than that of the comparative example, and the refrigerant is evenly distributed by the plurality of heat transfer tubes 45a. Therefore, the temperature threshold value Tb can be set to a temperature lower than the temperature threshold value Tc, and defrosting can be performed more efficiently than in the comparative example.
　本実施の形態２の冷凍サイクル装置１ｄは、除霜運転の際、第１熱源側熱交換器３に流入する冷媒を複数の伝熱管４５ａに分流する第１ガスヘッダ６１と、第２熱源側熱交換器４に流入する冷媒を複数の伝熱管４５ｂに分流する第２ガスヘッダ６３と有する。第１ガス配管４３ａは、重力方向に対して第１ガスヘッダ６１の中央部と接続され、第２ガス配管４３ｂは、重力方向に対して第２ガスヘッダ６３の中央部と接続される。 In the refrigeration cycle device 1d of the second embodiment, the first gas header 61 that divides the refrigerant flowing into the first heat source side heat exchanger 3 into the plurality of heat transfer tubes 45a during the defrosting operation, and the second heat source side heat. It has a second gas header 63 that divides the refrigerant flowing into the exchanger 4 into the plurality of heat transfer tubes 45b. The first gas pipe 43a is connected to the central portion of the first gas header 61 in the direction of gravity, and the second gas pipe 43b is connected to the central portion of the second gas header 63 in the direction of gravity.
　本実施の形態２において、除霜運転の際、実施の形態１において説明したように開閉弁７の開度を調整することで、第１熱源側熱交換器３および第２熱源側熱交換器４のそれぞれに流れる冷媒の流量が増加する。本実施の形態２によれば、伝熱管の高さの違いに起因して熱源側熱交換器の下段側に冷媒が滞留することが抑制され、下段側の冷媒の流量が増加する。その結果、熱源側熱交換器の下段側に付着した霜を確実、かつ効率的に除霜することができる。温度閾値ＴａおよびＴｂを比較例の温度閾値Ｔｃよりも小さい値に設定できるため、比較例に比べて除霜時間が短くなり、効率的に除霜できる。 In the second embodiment, the first heat source side heat exchanger 3 and the second heat source side heat exchanger are adjusted by adjusting the opening degree of the on-off valve 7 as described in the first embodiment during the defrosting operation. The flow rate of the refrigerant flowing in each of 4 increases. According to the second embodiment, it is suppressed that the refrigerant stays on the lower side of the heat source side heat exchanger due to the difference in the height of the heat transfer tube, and the flow rate of the refrigerant on the lower stage side increases. As a result, the frost adhering to the lower side of the heat source side heat exchanger can be reliably and efficiently removed. Since the temperature thresholds Ta and Tb can be set to values smaller than the temperature threshold Tc of the comparative example, the defrosting time is shorter than that of the comparative example, and defrosting can be performed efficiently.
実施の形態３．
　本実施の形態３の冷凍サイクル装置は、第１熱源側熱交換器の伝熱管の本数と第２熱源側熱交換器の伝熱管の本数とが異なる場合である。本実施の形態３においては、実施の形態１および２において説明した構成と同一の構成に同一の符号を付し、その詳細な説明を省略する。 Embodiment 3.
In the refrigeration cycle apparatus of the third embodiment, the number of heat transfer tubes of the first heat source side heat exchanger and the number of heat transfer tubes of the second heat source side heat exchanger are different. In the third embodiment, the same components as those described in the first and second embodiments are designated by the same reference numerals, and detailed description thereof will be omitted.
　本実施の形態３の冷凍サイクル装置の構成を説明する。図１８は、実施の形態３に係る冷凍サイクル装置の一構成例を示す冷媒回路図である。冷凍サイクル装置１ｅは、熱源側ユニット１０ｅを有する。熱源側ユニット１０ｅに設けられた第１熱源側熱交換器３は、第１分割熱交換器３－１および第２分割熱交換器３－２が並列に接続された構成である。 The configuration of the refrigeration cycle apparatus according to the third embodiment will be described. FIG. 18 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device according to the third embodiment. The refrigeration cycle device 1e has a heat source side unit 10e. The first heat source side heat exchanger 3 provided in the heat source side unit 10e has a configuration in which the first divided heat exchanger 3-1 and the second divided heat exchanger 3-2 are connected in parallel.
　第１ガス配管４３ａはガス分岐配管４３ａ－１および４３－２に分岐している。ガス分岐配管４３ａ－１は第１分割熱交換器３－１に接続され、ガス分岐配管４３ａ－２は第２分割熱交換器３－２に接続されている。第１液配管４４ａは液分岐配管４４ａ－１および４４ａ－２に分岐している。液分岐配管４４ａ－１は第１分割熱交換器３－１に接続され、液分岐配管４４ａ－２は第２分割熱交換器３－２に接続されている。 The first gas pipe 43a is branched into gas branch pipes 43a-1 and 43-2. The gas branch pipe 43a-1 is connected to the first split heat exchanger 3-1 and the gas branch pipe 43a-2 is connected to the second split heat exchanger 3-2. The first liquid pipe 44a is branched into liquid branch pipes 44a-1 and 44a-2. The liquid branch pipe 44a-1 is connected to the first split heat exchanger 3-1 and the liquid branch pipe 44a-2 is connected to the second split heat exchanger 3-2.
　第１分割熱交換器３－１において、ガス分岐配管４３ａ－１側に第１ガスヘッダ６１が設けられ、液分岐配管４４ａ－１側に第１液ヘッダ６２が設けられている。第２分割熱交換器３－２において、ガス分岐配管４３ａ－２側に第１ガスヘッダ６５が設けられ、液分岐配管４４ａ－２側に第１液ヘッダ６６が設けられている。第１ガスヘッダ６５は第１ガスヘッダ６１と同様な構成であり、第１液ヘッダ６６は第１液ヘッダ６２と同様な構成であるため、これらの詳細な説明を省略する。 In the first split heat exchanger 3-1 the first gas header 61 is provided on the gas branch pipe 43a-1 side, and the first liquid header 62 is provided on the liquid branch pipe 44a-1 side. In the second split heat exchanger 3-2, the first gas header 65 is provided on the gas branch pipe 43a-2 side, and the first liquid header 66 is provided on the liquid branch pipe 44a-2 side. Since the first gas header 65 has the same configuration as the first gas header 61 and the first liquid header 66 has the same configuration as the first liquid header 62, detailed description thereof will be omitted.
　図１９は、図１８に示した熱源側ユニットの一構成例を示す外観斜視図である。図２０は、図１８に示した熱源側ユニットについて、図１９の場合と異なる方向から見たときの外観斜視図である。第１分割熱交換器３－１および第２分割熱交換器３－２は、地面に対して垂直方向（Ｚ軸矢印方向）の長さである高さは同じであり、その高さをＬ１とする。第２熱源側熱交換器４の高さをＬ２とすると、高さＬ１およびＬ２は、Ｌ２＜Ｌ１の関係である。図１９および図２０に示す構成例は、例えば、Ｌ２＝Ｌ１×（２／３）の関係である。 FIG. 19 is an external perspective view showing a configuration example of the heat source side unit shown in FIG. FIG. 20 is an external perspective view of the heat source side unit shown in FIG. 18 when viewed from a direction different from that in the case of FIG. The first split heat exchanger 3-1 and the second split heat exchanger 3-2 have the same height, which is the length in the direction perpendicular to the ground (Z-axis arrow direction), and the height is L1. And. Assuming that the height of the second heat source side heat exchanger 4 is L2, the heights L1 and L2 have a relationship of L2 <L1. The configuration examples shown in FIGS. 19 and 20 have a relationship of, for example, L2 = L1 × (2/3).
　図２１は、図２０に示した熱源側ユニットを上から見たときの熱源側熱交換器のレイアウトを示す模式図である。第１分割熱交換器３－１および第２分割熱交換器３－２を上から見たときの形状は、図２１に示すように、Ｌ字状である。第２熱源側熱交換器４を上から見たときの形状は、図２１に示すように、直線状である。図２１に示す構成例において、第１分割熱交換器３－１はＬ字状であるが第１分割熱交換器３－１を直線状に伸ばした場合、第１分割熱交換器３－１の直線状の長さと第２熱源側熱交換器４の直線状の長さとは同等になる。 FIG. 21 is a schematic view showing the layout of the heat source side heat exchanger when the heat source side unit shown in FIG. 20 is viewed from above. As shown in FIG. 21, the shapes of the first split heat exchanger 3-1 and the second split heat exchanger 3-2 when viewed from above are L-shaped. As shown in FIG. 21, the shape of the second heat source side heat exchanger 4 when viewed from above is linear. In the configuration example shown in FIG. 21, the first split heat exchanger 3-1 is L-shaped, but when the first split heat exchanger 3-1 is extended in a straight line, the first split heat exchanger 3-1 The linear length of the second heat source side heat exchanger 4 is equal to the linear length of the second heat source side heat exchanger 4.
　図２２は、図１９に示した第１分割熱交換器の一構成例を示す側面図である。第２分割熱交換器３－２は第１分割熱交換器３－１と同じ構成であるため、図２２に示すことを省略している。また、図２２は、図２１に示したＬ字状の第１分割熱交換器３－１を直線状に伸ばした場合の状態を示す。図２３は、図２０に示した第２熱源側熱交換器の一構成例を示す側面図である。図２２および図２３には、説明の便宜上、方向を定義するためにＸ軸およびＺ軸を図に示しているが、Ｘ軸矢印は図１９および図２０に示したＸ軸矢印と対応していなくてもよい。 FIG. 22 is a side view showing a configuration example of the first split heat exchanger shown in FIG. Since the second split heat exchanger 3-2 has the same configuration as the first split heat exchanger 3-1, the description shown in FIG. 22 is omitted. Further, FIG. 22 shows a state in which the L-shaped first split heat exchanger 3-1 shown in FIG. 21 is linearly extended. FIG. 23 is a side view showing a configuration example of the second heat source side heat exchanger shown in FIG. In FIGS. 22 and 23, the X-axis and the Z-axis are shown in the drawings for convenience of explanation, but the X-axis arrows correspond to the X-axis arrows shown in FIGS. 19 and 20. It does not have to be.
　図２２に示す第１分割熱交換器３－１の伝熱管４５ａの本数は１３本である。図２３に示す第２熱源側熱交換器４の伝熱管４５ｂの本数は９本である。第１分割熱交換器３－１の伝熱管４５ａの本数の方が第２熱源側熱交換器４の伝熱管４５ｂの本数よりも多い。第１分割熱交換器３－１の伝熱管４５ａの本数と第２熱源側熱交換器４の伝熱管４５ｂの本数との比は、第１熱源側熱交換器３の高さＬ１と第２熱源側熱交換器４の高さＬ２との比（Ｌ１：Ｌ２）＝３：２に近い値になっている。 The number of heat transfer tubes 45a of the first split heat exchanger 3-1 shown in FIG. 22 is 13. The number of heat transfer tubes 45b of the second heat source side heat exchanger 4 shown in FIG. 23 is nine. The number of heat transfer tubes 45a of the first split heat exchanger 3-1 is larger than the number of heat transfer tubes 45b of the second heat source side heat exchanger 4. The ratio of the number of heat transfer tubes 45a of the first split heat exchanger 3-1 to the number of heat transfer tubes 45b of the second heat source side heat exchanger 4 is the height L1 of the first heat source side heat exchanger 3 and the second. The ratio (L1: L2) of the heat source side heat exchanger 4 to the height L2 is close to 3: 2.
　本実施の形態３において、図２２に示す伝熱管４５ａの長さと図２３に示す伝熱管４５ｂの長さとが同じと仮定して、第１熱源側熱交換器３および第２熱源側熱交換器４について、除霜対象の伝熱管の本数を比べてみる。第１分割熱交換器３－１の伝熱管４５ａの本数は、Ｌ１／Ｌ２の比から、第２熱源側熱交換器４の伝熱管４５ｂの本数の（３／２）倍である。第１分割熱交換器３－１および第２分割熱交換器３－２は伝熱管４５ａの本数が同じなので、第１熱源側熱交換器３の伝熱管４５ａの本数は第２熱源側熱交換器４の伝熱管４５ｂの本数の３倍となる。なお、第１分割熱交換器３－１および第２分割熱交換器３－２の伝熱管４５ａの本数と、第２熱源側熱交換器４の伝熱管４５ｂの本数とは、図２２および図２３に示した場合に限らない。 In the third embodiment, assuming that the length of the heat transfer tube 45a shown in FIG. 22 and the length of the heat transfer tube 45b shown in FIG. 23 are the same, the first heat source side heat exchanger 3 and the second heat source side heat exchanger 3 For 4, compare the number of heat transfer tubes to be defrosted. The number of heat transfer tubes 45a of the first split heat exchanger 3-1 is (3/2) times the number of heat transfer tubes 45b of the second heat source side heat exchanger 4 from the ratio of L1 / L2. Since the first split heat exchanger 3-1 and the second split heat exchanger 3-2 have the same number of heat transfer tubes 45a, the number of heat transfer tubes 45a of the first heat source side heat exchanger 3 is the second heat source side heat exchange. This is three times the number of heat transfer tubes 45b of the vessel 4. The number of heat transfer tubes 45a of the first split heat exchanger 3-1 and the second split heat exchanger 3-2 and the number of heat transfer tubes 45b of the second heat source side heat exchanger 4 are shown in FIGS. 22 and 22. It is not limited to the case shown in 23.
　なお、本実施の形態３の冷凍サイクル装置１ｅの動作は、図５を参照して説明した動作手順と同様になるため、その詳細な説明を省略する。 Since the operation of the refrigeration cycle device 1e according to the third embodiment is the same as the operation procedure described with reference to FIG. 5, detailed description thereof will be omitted.
　図５を参照すると、ステップＳ１０２の処理による除霜運転の開始から時間ｔ１が時間閾値ｔｔｈ１に到達するまで、開閉弁７が閉じているため、第１熱源側熱交換器３の除霜が集中的に行われる。その後、開閉弁７が開き、第２熱源側熱交換器４の除霜が開示されるが、第１熱源側熱交換器３にも冷媒が流れる。第１熱源側熱交換器３に流れる冷媒の量が第２熱源側熱交換器４に流れる冷媒の量よりも多くなる。そのため、第１熱源側熱交換器３の伝熱管４５ａの本数が第２熱源側熱交換器４の伝熱管４５ｂの本数よりも多くても、冷凍サイクル装置１ｅは、第２熱源側熱交換器４の除霜終了のタイミングに合わせて、第１熱源側熱交換器３の除霜を終了させることができる。 Referring to FIG. 5, since the on-off valve 7 is closed from the start of the defrosting operation by the process of step S102 until the time t1 reaches the time threshold value tth1, the defrosting of the first heat source side heat exchanger 3 is concentrated. Is done. After that, the on-off valve 7 opens, and defrosting of the second heat source side heat exchanger 4 is disclosed, but the refrigerant also flows to the first heat source side heat exchanger 3. The amount of the refrigerant flowing through the first heat source side heat exchanger 3 is larger than the amount of the refrigerant flowing through the second heat source side heat exchanger 4. Therefore, even if the number of heat transfer tubes 45a of the first heat source side heat exchanger 3 is larger than the number of heat transfer tubes 45b of the second heat source side heat exchanger 4, the refrigeration cycle device 1e is the second heat source side heat exchanger. The defrosting of the first heat source side heat exchanger 3 can be completed at the timing of the completion of defrosting of 4.
　本実施の形態３の冷凍サイクル装置１ｅは、第１熱源側熱交換器３の伝熱管４５ａの本数が第２熱源側熱交換器４の伝熱管の本数よりも多い。本実施の形態３によれば、第１熱源側熱交換器３に流れる冷媒の量が第２熱源側熱交換器４に流れる冷媒の量よりも多いため、第２熱源側熱交換器４の除霜終了のタイミングに合わせて、第１熱源側熱交換器３の除霜を終了させることができる。 In the refrigeration cycle device 1e of the third embodiment, the number of heat transfer tubes 45a of the first heat source side heat exchanger 3 is larger than the number of heat transfer tubes of the second heat source side heat exchanger 4. According to the third embodiment, since the amount of the refrigerant flowing in the first heat source side heat exchanger 3 is larger than the amount of the refrigerant flowing in the second heat source side heat exchanger 4, the second heat source side heat exchanger 4 The defrosting of the first heat source side heat exchanger 3 can be completed at the timing of the end of defrosting.
（変形例４）
　変形例４の冷凍サイクル装置は、図１８に示した冷媒回路６０ａおよび６０ｂにおいて、第１液配管４４ａに流量調整弁９が設けられた場合である。変形例４においては、図１８～図２３を参照して説明した構成と同一の構成に同一の符号を付し、その詳細な説明を省略する。 (Modification example 4)
The refrigeration cycle device of the modified example 4 is a case where the flow rate adjusting valve 9 is provided in the first liquid pipe 44a in the refrigerant circuits 60a and 60b shown in FIG. In the fourth modification, the same components as those described with reference to FIGS. 18 to 23 are designated by the same reference numerals, and detailed description thereof will be omitted.
　変形例４の冷凍サイクル装置の構成を説明する。図２４は、変形例４の冷凍サイクル装置の一構成例を示す冷媒回路図である。冷凍サイクル装置１ｆの熱源側ユニット１０ｆにおいて、第１液配管４４ａに流量調整弁９が設けられている。 The configuration of the refrigeration cycle device of the modified example 4 will be described. FIG. 24 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device of the modified example 4. In the heat source side unit 10f of the refrigeration cycle device 1f, the flow rate adjusting valve 9 is provided in the first liquid pipe 44a.
　なお、冷凍サイクル装置１ｆの動作は、図１０に示すステップＳ２０７において、タイマ５３によって計測される時間ｔ１に基づいて、除霜対象の切り替えのタイミングを決定することを除いて、図１０に示した手順と同様になるため、その詳細な説明を省略する。冷媒温度センサ１２は、第２液配管４４ｂの代わりに、第１液配管４４ａおよび第２液配管４４ｂの合流点に近い液配管４７に設けられていてもよい。 The operation of the refrigeration cycle device 1f is shown in FIG. 10 except that the timing of switching the defrost target is determined based on the time t1 measured by the timer 53 in step S207 shown in FIG. Since the procedure is the same, the detailed description thereof will be omitted. The refrigerant temperature sensor 12 may be provided in the liquid pipe 47 near the confluence of the first liquid pipe 44a and the second liquid pipe 44b instead of the second liquid pipe 44b.
　変形例４によれば、第１熱源側熱交換器３および第２熱源側熱交換器４のそれぞれの液配管に冷媒の流通を遮断する弁が設けられている。変形例４の冷凍サイクル装置１ｆが、除霜運転の際、各弁の開閉を制御して、はじめに第１熱源側熱交換器３を除霜した後、残りの第２熱源側熱交換器４を除霜することで、確実、かつ効率よく除霜を行うことができる。 According to the modified example 4, a valve for shutting off the flow of the refrigerant is provided in each of the liquid pipes of the first heat source side heat exchanger 3 and the second heat source side heat exchanger 4. The refrigeration cycle device 1f of the modified example 4 controls the opening and closing of each valve during the defrosting operation to first defrost the first heat source side heat exchanger 3, and then the remaining second heat source side heat exchanger 4 By defrosting, defrosting can be performed reliably and efficiently.
　なお、本実施の形態３において、実施の形態２で説明した冷凍サイクル装置１ｄをベースに説明したが、本実施の形態３を実施の形態１で説明した冷凍サイクル装置１に適用してもよい。また、実施の形態２および３の各実施の形態において、変形例１～３のうち、いずれの変形例を組み合わせてもよい。 Although the description of the third embodiment is based on the refrigeration cycle device 1d described in the second embodiment, the third embodiment may be applied to the refrigeration cycle device 1 described in the first embodiment. .. Further, in each of the second and third embodiments, any of the modified examples 1 to 3 may be combined.
　１、１ａ～１ｆ　冷凍サイクル装置、２　圧縮機、３　第１熱源側熱交換器、３－１　第１分割熱交換器、３－２　第２分割熱交換器、４　第２熱源側熱交換器、５　流路切替装置、６　アキュムレータ、７　開閉弁、８　第３熱源側熱交換器、９　流量調整弁、９ａ　第１流量調整弁、９ｂ　第２流量調整弁、１０ａ～１０ｆ　熱源側ユニット、１１　熱交換器温度センサ、１２、１２ａ～１２ｃ　冷媒温度センサ、１５　熱源側熱交換器、２０ａ、２０ｂ　負荷側ユニット、２１ａ、２１ｂ　負荷側熱交換器、２２ａ、２２ｂ　膨張弁、２３ａ、２３ｂ　室温センサ、３０　制御装置、３１　処理回路、４１　ガス配管、４２　冷媒配管、４３ａ　第１ガス配管、４３ａ－１、４３ａ－２　ガス分岐配管、４３ｂ　第２ガス配管、４３ｃ　第３ガス配管、４４ａ　第１液配管、４４ａ－１、４４ａ－２　液分岐配管、４４ｂ　第２液配管、４４ｃ　第３液配管、４５ａ、４５ｂ　伝熱管、４６ａ、４６ｂ　放熱フィン、４７　液配管、４８、４９　冷媒配管、５１　冷凍サイクル制御手段、５２　判定手段、５３　タイマ、５４　第１除霜手段、５５　第２除霜手段、６０ａ、６０ｂ　冷媒回路、６１　第１ガスヘッダ、６２　第１液ヘッダ、６３　第２ガスヘッダ、６４　第２液ヘッダ、６５　第１ガスヘッダ、６６　第１液ヘッダ、７１　プロセッサ、７２　メモリ、１００　冷凍サイクル装置、１１０　熱源側ユニット、１２１　冷媒温度センサ、１３０　制御装置。 1, 1a-1f Refrigeration cycle device, 2 Compressor, 3 1st heat source side heat exchanger, 3-1 1st split heat exchanger, 3-2 2nd split heat exchanger, 4 2nd heat source side heat exchanger 5, Flow path switching device, 6 Accumulator, 7 On-off valve, 8 Third heat source side heat exchanger, 9 Flow control valve, 9a 1st flow control valve, 9b 2nd flow control valve, 10a to 10f Heat source side unit, 11 Heat exchanger temperature sensor, 12, 12a-12c Refrigerant temperature sensor, 15 Heat source side heat exchanger, 20a, 20b Load side unit, 21a, 21b Load side heat exchanger, 22a, 22b Expansion valve, 23a, 23b Room temperature sensor, 30 Control device, 31 Processing circuit, 41 Gas pipe, 42 Refrigerant pipe, 43a 1st gas pipe, 43a-1, 43a-2 Gas branch pipe, 43b 2nd gas pipe, 43c 3rd gas pipe, 44a 1st liquid pipe , 44a-1, 44a-2 liquid branch pipe, 44b second liquid pipe, 44c third liquid pipe, 45a, 45b heat transfer pipe, 46a, 46b heat dissipation fin, 47 liquid pipe, 48, 49 refrigerant pipe, 51 refrigeration cycle control Means, 52 Judgment means, 53 Timer, 54 1st defrosting means, 55 2nd defrosting means, 60a, 60b Refrigerant circuit, 61 1st gas header, 62 1st liquid header, 63 2nd gas header, 64 2nd liquid header , 65 1st gas header, 66 1st liquid header, 71 processor, 72 memory, 100 refrigeration cycle device, 110 heat source side unit, 121 refrigerant temperature sensor, 130 control device.

Claims (8)

  1. 　冷媒を圧縮して吐出する圧縮機と、
    　前記冷媒を減圧して膨張させる膨張弁と、
    　前記膨張弁と接続される負荷側熱交換器と、
    　前記圧縮機および前記負荷側熱交換器と接続される流路切替装置と、
    　前記流路切替装置と前記膨張弁との間において並列に接続される第１熱源側熱交換器および第２熱源側熱交換器を含む熱源側熱交換器と、
    　除霜運転時に流通する前記冷媒の前記第２熱源側熱交換器の下流側に設けられた開閉弁と、
    　前記除霜運転を行う際、前記圧縮機から吐出される前記冷媒が前記熱源側熱交換器に流入するように前記流路切替装置を制御する制御装置と、
    を有し、
    　前記制御装置は、
    　前記除霜運転が開始されるとき、前記開閉弁を開状態から閉状態に切り替える第１除霜手段と、
    　除霜対象の切り替えのタイミングを決定する判定手段と、
    　前記判定手段によって決定される前記タイミングにしたがって、前記開閉弁を閉状態から開状態に切り替える第２除霜手段と、を有する、
    　冷凍サイクル装置。     A compressor that compresses and discharges the refrigerant,
    An expansion valve that decompresses and expands the refrigerant,
    The load side heat exchanger connected to the expansion valve and
    A flow path switching device connected to the compressor and the load side heat exchanger,
    A heat source side heat exchanger including a first heat source side heat exchanger and a second heat source side heat exchanger connected in parallel between the flow path switching device and the expansion valve.
    An on-off valve provided on the downstream side of the second heat source side heat exchanger of the refrigerant distributed during the defrosting operation, and
    A control device that controls the flow path switching device so that the refrigerant discharged from the compressor flows into the heat source side heat exchanger during the defrosting operation.
    Have,
    The control device is
    When the defrosting operation is started, the first defrosting means for switching the on-off valve from the open state to the closed state, and
    Judgment means for determining the timing of switching the defrost target,
    It has a second defrosting means for switching the on-off valve from the closed state to the open state according to the timing determined by the determination means.
    Refrigeration cycle equipment.
  2. 　前記第１熱源側熱交換器は、前記流路切替装置を介して前記圧縮機から前記冷媒が流入する複数の第１伝熱管を有し、
    　前記第２熱源側熱交換器は、前記流路切替装置を介して前記圧縮機から前記冷媒が流入する複数の第２伝熱管を有し、
    　前記複数の第１伝熱管の本数は、前記複数の第２伝熱管の本数よりも多い、
    　請求項１に記載の冷凍サイクル装置。     The first heat source side heat exchanger has a plurality of first heat transfer tubes into which the refrigerant flows from the compressor via the flow path switching device.
    The second heat source side heat exchanger has a plurality of second heat transfer tubes into which the refrigerant flows from the compressor via the flow path switching device.
    The number of the plurality of first heat transfer tubes is larger than the number of the plurality of second heat transfer tubes.
    The refrigeration cycle apparatus according to claim 1.
  3. 　前記第１熱源側熱交換器と接続される第１ガス配管と、前記第２熱源側熱交換器と接続される第２ガス配管とを合流して前記流路切替装置に接続するガス配管と、
    　前記圧縮機から前記第１熱源側熱交換器に流入する前記冷媒を前記複数の第１伝熱管に分流する第１ガスヘッダと、
    　前記圧縮機から前記第２熱源側熱交換器に流入する前記冷媒を前記複数の第２伝熱管に分流する第２ガスヘッダと、をさらに有し、
    　前記第１ガス配管は、重力方向に対して前記第１ガスヘッダの中央部と接続され、
    　前記第２ガス配管は、前記重力方向に対して前記第２ガスヘッダの中央部と接続される、
    　請求項２に記載の冷凍サイクル装置。     A gas pipe that joins the first gas pipe connected to the first heat source side heat exchanger and the second gas pipe connected to the second heat source side heat exchanger and connects to the flow path switching device. ,
    A first gas header that divides the refrigerant flowing from the compressor into the first heat source side heat exchanger into the plurality of first heat transfer tubes, and
    Further, it has a second gas header that divides the refrigerant flowing from the compressor into the second heat source side heat exchanger into the plurality of second heat transfer tubes.
    The first gas pipe is connected to the central portion of the first gas header in the direction of gravity.
    The second gas pipe is connected to the central portion of the second gas header in the direction of gravity.
    The refrigeration cycle apparatus according to claim 2.
  4. 　前記第２熱源側熱交換器の前記下流側に設けられ、前記冷媒の温度を検出する温度センサをさらに有し、
    　前記判定手段は、
    　前記温度センサの検出値が予め決められた温度閾値以上になるときを、前記タイミングに決定する、
    　請求項１～３のいずれか１項に記載の冷凍サイクル装置。     Further, a temperature sensor provided on the downstream side of the second heat source side heat exchanger and detecting the temperature of the refrigerant is provided.
    The determination means
    When the detection value of the temperature sensor becomes equal to or higher than a predetermined temperature threshold value, the timing is determined.
    The refrigeration cycle apparatus according to any one of claims 1 to 3.
  5. 　前記除霜運転時に流通する前記冷媒の前記第１熱源側熱交換器の下流側に設けられた流量調整弁をさらに有し、
    　前記第１除霜手段は、前記除霜運転が開始されるとき、前記流量調整弁の開状態を維持し、前記開閉弁を開状態から閉状態に切り替え、
    　前記第２除霜手段は、前記判定手段によって決定される前記タイミングにしたがって、前記流量調整弁を開状態から閉状態に切り替え、前記開閉弁を閉状態から開状態に切り替える、
    　請求項１～３のいずれか１項に記載の冷凍サイクル装置。     Further having a flow rate adjusting valve provided on the downstream side of the first heat source side heat exchanger of the refrigerant flowing during the defrosting operation.
    When the defrosting operation is started, the first defrosting means maintains the open state of the flow rate adjusting valve and switches the on-off valve from the open state to the closed state.
    The second defrosting means switches the flow rate adjusting valve from the open state to the closed state and switches the on-off valve from the closed state to the open state according to the timing determined by the determination means.
    The refrigeration cycle apparatus according to any one of claims 1 to 3.
  6. 　前記第１熱源側熱交換器の前記下流側に設けられ、前記冷媒の温度を検出する温度センサをさらに有し、
    　前記判定手段は、
    　前記温度センサの検出値が予め決められた温度閾値以上になるときを、前記タイミングに決定する、
    　請求項５に記載の冷凍サイクル装置。     Further, a temperature sensor provided on the downstream side of the first heat source side heat exchanger and detecting the temperature of the refrigerant is provided.
    The determination means
    When the detection value of the temperature sensor becomes equal to or higher than a predetermined temperature threshold value, the timing is determined.
    The refrigeration cycle apparatus according to claim 5.
  7. 　前記制御装置は、時間を計測するタイマをさらに有し、
    　前記判定手段は、
    　前記除霜運転の開始から前記タイマによって計測される時間が予め決められた時間閾値以上になるときを、前記タイミングに決定する、
    　請求項１～３および５のいずれか１項に記載の冷凍サイクル装置。     The control device further includes a timer for measuring time.
    The determination means
    The timing is determined when the time measured by the timer from the start of the defrosting operation becomes equal to or greater than a predetermined time threshold value.
    The refrigeration cycle apparatus according to any one of claims 1 to 3 and 5.
  8. 　前記流路切替装置と前記膨張弁との間において前記第１熱源側熱交換器および前記第２熱源側熱交換器と並列に接続される第３熱源側熱交換器と、
    　前記除霜運転時に流通する前記冷媒の前記第１熱源側熱交換器の下流側に設けられた第１流量調整弁と、
    　前記除霜運転時に流通する前記冷媒の前記第３熱源側熱交換器の下流側に設けられた第２流量調整弁と、をさらに有し、
    　前記第１除霜手段は、
    　前記除霜運転が開始されるとき、前記第１流量調整弁の開状態を維持し、前記開閉弁および前記第２流量調整弁を開状態から閉状態に切り替え、
    　前記第２除霜手段は、
    　前記判定手段によって決定される前記タイミングにしたがって、前記第１流量調整弁を開状態から閉状態に切り替え、前記開閉弁を閉状態から開状態に切り替え、
    　前記第２除霜手段は、
    　前記開閉弁を閉状態から開状態に切り替えた後、前記判定手段によって決定される前記タイミングにしたがって、前記開閉弁を開状態から閉状態に切り替え、前記第２流量調整弁を閉状態から開状態に切り替える、
    　請求項１に記載の冷凍サイクル装置。     A third heat source side heat exchanger connected in parallel with the first heat source side heat exchanger and the second heat source side heat exchanger between the flow path switching device and the expansion valve.
    A first flow rate adjusting valve provided on the downstream side of the first heat source side heat exchanger of the refrigerant flowing during the defrosting operation, and
    Further, it has a second flow rate adjusting valve provided on the downstream side of the third heat source side heat exchanger of the refrigerant flowing during the defrosting operation.
    The first defrosting means is
    When the defrosting operation is started, the open state of the first flow rate adjusting valve is maintained, and the on-off valve and the second flow rate adjusting valve are switched from the open state to the closed state.
    The second defrosting means
    According to the timing determined by the determination means, the first flow rate adjusting valve is switched from the open state to the closed state, and the on-off valve is switched from the closed state to the open state.
    The second defrosting means
    After switching the on-off valve from the closed state to the open state, the on-off valve is switched from the open state to the closed state according to the timing determined by the determination means, and the second flow rate adjusting valve is switched from the closed state to the open state. Switch to,
    The refrigeration cycle apparatus according to claim 1.
PCT/JP2019/044375 2019-11-12 2019-11-12 Refrigeration cycle device WO2021095124A1 (en)

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Citations (6)

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JPH04344085A (en) * 1991-05-17 1992-11-30 Daikin Ind Ltd Defrosting operation control device for refrigerating apparatus
JPH11304309A (en) * 1998-04-20 1999-11-05 Fujitsu General Ltd Air conditioner
JP2002089980A (en) * 2000-09-20 2002-03-27 Fujitsu General Ltd Air conditioner
JP2008039298A (en) * 2006-08-07 2008-02-21 Denso Corp Heat pump cycle
JP2015224829A (en) * 2014-05-28 2015-12-14 ダイキン工業株式会社 Refrigeration device
WO2016001957A1 (en) * 2014-06-30 2016-01-07 日立アプライアンス株式会社 Air conditioner

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Publication number Priority date Publication date Assignee Title
DE69824969T2 (en) 1997-11-20 2005-08-04 Glasstech, Inc., Perrysburg MOLDING ARRANGEMENT FOR SHAPES FOR FORMING HEATED GLASS PANES

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04344085A (en) * 1991-05-17 1992-11-30 Daikin Ind Ltd Defrosting operation control device for refrigerating apparatus
JPH11304309A (en) * 1998-04-20 1999-11-05 Fujitsu General Ltd Air conditioner
JP2002089980A (en) * 2000-09-20 2002-03-27 Fujitsu General Ltd Air conditioner
JP2008039298A (en) * 2006-08-07 2008-02-21 Denso Corp Heat pump cycle
JP2015224829A (en) * 2014-05-28 2015-12-14 ダイキン工業株式会社 Refrigeration device
WO2016001957A1 (en) * 2014-06-30 2016-01-07 日立アプライアンス株式会社 Air conditioner

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