WO2015083392A1 - Dispositif de pompe à chaleur - Google Patents

Dispositif de pompe à chaleur Download PDF

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Publication number
WO2015083392A1
WO2015083392A1 PCT/JP2014/067592 JP2014067592W WO2015083392A1 WO 2015083392 A1 WO2015083392 A1 WO 2015083392A1 JP 2014067592 W JP2014067592 W JP 2014067592W WO 2015083392 A1 WO2015083392 A1 WO 2015083392A1
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Prior art keywords
sub
heat exchange
refrigerant
heat
exchange unit
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PCT/JP2014/067592
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English (en)
Japanese (ja)
Inventor
藤塚　正史
和典 土野
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三菱電機株式会社
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Publication of WO2015083392A1 publication Critical patent/WO2015083392A1/fr

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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
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F25B2347/021—Alternate defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a heat pump device including a refrigerant circuit.
  • Patent Document 1 a plurality of first switching valves 25 provided between an outlet side of the outdoor heat exchangers 22 installed in parallel and a suction side of the compressor 21, and the outdoor heat exchangers 22 are arranged.
  • An air conditioner including a second switching valve 26 provided between the outlet side and the discharge side of the compressor 21 is disclosed.
  • This patent document 1 discloses that in the outdoor heat exchanger 22 where defrosting is required, by opening the first switching valve 25 and closing the second switching valve 26, only the outdoor heat exchanger 22 is supplied from the compressor 21. The discharged hot gas refrigerant flows and defrosts.
  • Patent Document 2 discloses a showcase in which a cooling operation is performed by the first evaporator 15c and the second evaporator 16c.
  • the high-temperature refrigerant discharged from the compressor 14a circulates in the condenser 14b and dissipates heat, and then does not pass through the expansion valve 23. It distribute
  • Patent Document 2 intends to perform a defrost cooling operation in which the first evaporator 15c is defrosted while the inside of the showcase is cooled by the second evaporator 16c.
  • JP 2008-157558 A (FIG. 4, pages 7 to 8) JP 2008-133998 A (FIG. 6, page 5)
  • the air conditioner disclosed in Patent Document 1 causes the refrigerant to flow in parallel to the plurality of outdoor heat exchangers 22 in a normal heating operation without defrosting, but in the heating operation with defrosting, the defrosting is performed.
  • the refrigerant flowing through the outdoor heat exchanger 22 having the request is circulated in series to the outdoor heat exchanger 22 having no defrosting request.
  • the distribution route of the refrigerant is complicated, and a large number of switching valves are required for switching the complicated distribution route. Therefore, there are problems that it is difficult to reduce the size of the apparatus, the cost is high, and the failure rate is high and the reliability is low.
  • the present invention was made against the background of the above problems, and is small, inexpensive, highly reliable, suppresses refrigerant accumulation, has high energy savings, and is comfortable during defrosting or food storage quality.
  • the heat pump apparatus which keeps up is provided.
  • the heat pump device includes a refrigerant circuit in which a compressor, a first heat exchange unit, an expansion device, and a second heat exchanger are connected by a pipe and through which refrigerant flows, and a control unit that controls the operation of the refrigerant circuit.
  • the first heat exchange unit has a plurality of sub heat exchange units connected in series, and a sub expansion device provided between the plurality of sub heat exchange units,
  • the control unit defrosts the sub-heat exchange unit
  • the sub-expansion device causes a difference between the pressure of the refrigerant flowing upstream of the sub-expansion device and the pressure of the refrigerant flowing downstream of the sub-expansion device. It has the control means at the time of defrosting which controls.
  • the defrosting control means defrosts the auxiliary heat exchange unit
  • the pressure difference between the refrigerant flowing upstream of the auxiliary expansion device and the refrigerant flowing downstream of the auxiliary expansion device is calculated.
  • heating, cooling, or cooling is continued by the other subheat exchange part, defrosting at least one subheat exchange part.
  • comfort and food preservation quality are not impaired at the time of defrosting.
  • these effects can be obtained while saving the effort of switching the operation mode, being small, inexpensive, and highly reliable, suppressing the accumulation of refrigerant, and providing high energy savings.
  • FIG. 1 is a schematic diagram showing a heat pump device 1 according to Embodiment 1.
  • FIG. 4 is a schematic diagram showing a heat pump device 1 according to Embodiment 2.
  • FIG. 6 is a schematic diagram showing a heat pump device 200 according to Embodiment 3.
  • FIG. 6 is a schematic diagram showing a first heat exchange unit 4 in Embodiment 4.
  • FIG. 10 is a schematic diagram showing a first heat exchange unit 4 in a fifth embodiment.
  • FIG. 10 is a schematic diagram showing a first heat exchange unit 4 in a sixth embodiment.
  • FIG. 10 is a schematic diagram showing a second sub heat exchange unit 42 in a sixth embodiment.
  • FIG. 10 is a schematic diagram showing a heat pump device 500 according to a sixth embodiment.
  • FIG. 10 is a schematic diagram showing a heat pump device 600 according to a seventh embodiment.
  • FIG. 1 is a schematic diagram showing a heat pump device 1 according to the first embodiment.
  • the heat pump device 1 will be described with reference to FIG.
  • the heat pump device 1 constituting an air conditioner or the like includes a refrigerant circuit 8 and a control unit 21.
  • the refrigerant circuit 8 is a circuit in which the compressor 2, the first heat exchange unit 4, the expansion device 6, and the second heat exchanger 7 are connected by piping, and the refrigerant circulates.
  • coolant to be used is a refrigerant
  • the refrigerant circuit 8 absorbs heat from, for example, one of the outdoor air 11 and the indoor air 12 and dissipates heat to the other using the condensation and vaporization of the circulating refrigerant.
  • the outdoor air 11 is air as a heat absorption source (during heating operation) or a heat radiation destination (during cooling operation) necessary for cooling and heating the indoor air 12.
  • heat is efficiently transferred between the outdoor air 11 and the indoor air 12 via the refrigerant with respect to the power required for the compression of the compressor 2.
  • the refrigerant that has been reduced in temperature and pressure by the expansion device 6 to be in a gas-liquid two-phase state flows to the second heat exchanger 7 installed in the room.
  • the refrigerant that has become a high-temperature and high-pressure state in the compressor 2 and is in a gas phase flows through the second heat exchanger 7.
  • the refrigerant flow direction in the refrigerant circuit 8 is reversed when the indoor air 12 is cooled or heated.
  • the compressor 2 pumps the refrigerant in a gas phase to increase the temperature and pressure.
  • a pressure feed switching unit 3 is provided on the discharge side of the compressor 2.
  • the pressure feed switching unit 3 switches the refrigerant flow direction in the refrigerant circuit 8.
  • This pressure feed switching unit 3 is, for example, a four-way valve, and four connection paths A, B, C, and D are connected to the four-way valve.
  • the pumping switching unit 3 is connected in the first state in which the connection path A and the connection path B, the connection path C and the connection path D are connected, the connection path A and the connection path C, and the connection path B and the connection path D are connected.
  • the second state can be changed to the second state.
  • connection path A is connected to the discharge side of the compressor 2
  • connection path B is connected to the second heat exchanger 7
  • connection path C is connected to the first heat exchange unit 4
  • connection path D is It is connected to the suction side of the compressor 2.
  • the first heat exchange unit 4 is used outdoors. For example, the outdoor air 11 blown by a fan (not shown) is used as a heat source to exchange heat between the outdoor air 11 and the refrigerant. .
  • the 1st heat exchange unit 4 is provided with the 1st sub heat exchange part 41 and the 2nd sub heat exchange part 42, and these 1st sub heat exchange parts 41 and the 2nd sub heat exchange part 42 is connected in series. Thereby, the refrigerant does not flow in the parallel direction but always flows in the series direction in the first sub heat exchange unit 41 and the second sub heat exchange unit 42.
  • the number of sub heat exchange units is not limited to two, and a plurality of sub heat exchange units may be installed.
  • a sub-expansion device 43 is provided between the first sub-heat exchange unit 41 and the second sub-heat exchange unit 42.
  • the sub-expansion device 43 is a high-pressure liquid-phase refrigerant. Is expanded to lower the temperature and pressure to make a gas-liquid two-phase refrigerant.
  • the sub-expansion device 43 is, for example, an expansion valve that changes the amount of refrigerant flow and the pressure of the refrigerant according to the degree of opening. Since the sub-expansion device 43 is provided between the first sub-heat exchange unit 41 and the second sub-heat exchange unit 42, the refrigerant flowing through the first heat exchange unit 4 is always sub-expansion. Flows into the device 43.
  • the refrigerant circuit 8 is provided with a sub-bypass circuit 44 that bypasses the sub-expansion device 43, and the sub-bypass circuit 44 is provided with a sub-bypass valve 45 that adjusts the amount of refrigerant flowing in the sub-bypass circuit 44. It has been.
  • the sub bypass valve 45 When the sub bypass valve 45 is closed, all the refrigerant flowing through the first heat exchange unit 4 does not flow into the sub bypass circuit 44 but flows into the sub expansion device 43.
  • the sub bypass valve 45 is opened, the refrigerant flowing through the first heat exchange unit 4 flows into the sub bypass circuit 44 and the sub expansion device 43 separately. At this time, if the sub-expansion device 43 is throttled, the refrigerant flowing into the sub-expansion device 43 decreases, and a large amount of the remaining refrigerant flows into the sub-bypass circuit 44.
  • the inflow switching unit 5 is a four-way valve, for example, similarly to the pressure-feeding switching unit 3, and the four connection paths A, B, C, and D are connected to the four-way valve.
  • the inflow switching unit 5 includes the first state in which the connection path A and the connection path B, the connection path C and the connection path D are connected, the connection path A and the connection path C, and the connection path B and the connection path D are connected.
  • the second state can be changed to the second state.
  • the connection path A is connected to the expansion device 6,
  • the connection path B is connected to the first auxiliary heat exchange unit 41,
  • the connection path C is connected to the second auxiliary heat exchange unit 42, and the connection path D is pumped. It is connected to the switching unit 3.
  • the refrigerant By switching the inflow switching unit 5, when the refrigerant flows into the first heat exchange unit 4, the refrigerant first flows into the first sub heat exchange unit 41 and then flows into the second sub heat exchange unit 42. Or, first, it is changed whether it flows into the 2nd sub heat exchange part 42, and flows into the 1st sub heat exchange part 41 after that. Further, by switching the inflow switching unit 5, the refrigerant flowing out from the first heat exchange unit 4 to the side opposite to the inflow source flows into the suction side of the compressor 2 or flows into the expansion device 6. Is changed.
  • the refrigerant circuit 8 includes two first temperature detection units 41a and a second temperature detection unit 42a that detect the temperature of the refrigerant.
  • the first sub heat exchange unit 41 and the sub expansion device 43 are provided.
  • the second auxiliary heat exchanging unit 42 and the auxiliary expansion device 43 are provided.
  • the first temperature detector 41a and the second temperature detector 42a indirectly detect the temperature of the refrigerant by measuring the temperature of the pipe.
  • the expansion device 6 expands a high-pressure liquid-phase refrigerant to lower the temperature and the pressure to obtain a gas-liquid two-phase refrigerant.
  • the expansion device 6 is, for example, an expansion valve that changes the flow rate of the refrigerant and the pressure of the refrigerant at the opening degree.
  • the refrigerant circuit 8 is provided with a bypass circuit 61 that bypasses the expansion device 6, and the bypass circuit 61 is provided with a bypass valve 62 that adjusts the amount of refrigerant flowing in the bypass circuit 61.
  • the bypass valve 62 When the bypass valve 62 is closed, all the refrigerant flowing through the refrigerant circuit 8 does not flow into the bypass circuit 61 but flows into the expansion device 6.
  • the bypass valve 62 when the bypass valve 62 is opened, the refrigerant flowing through the refrigerant circuit 8 flows into the bypass circuit 61 and the expansion device 6 separately. At this time, if the expansion device 6 is throttled, the refrigerant flowing into the expansion device 6 decreases, and the remaining large amount of refrigerant flows into the bypass circuit 61.
  • the second heat exchanger 7 is used indoors.
  • the indoor heat 12 blown by a fan (not shown) is used as a heat source, and load heat exchange is performed to exchange heat between the indoor air 12 and the refrigerant. It is a vessel.
  • Control unit 21 The controller 21 controls the operation of the refrigerant circuit 8.
  • the control unit 21 includes a defrosting control unit 22, a threshold determination unit 23, and an end determination unit 24.
  • the defrosting control means 22 can also be configured to open the bypass valve 62 when defrosting the first sub heat exchange unit 41 or the second sub heat exchange unit 42. Further, the defrosting control means 22 may be configured to close the sub bypass valve 45 when the first sub heat exchange unit 41 or the second sub heat exchange unit 42 is defrosted. In addition, the defrosting control means 22 can also control the operation of the expansion device 6.
  • the threshold value determination unit 23 determines whether or not the temperature of the refrigerant detected by the first temperature detection unit 41a or the second temperature detection unit 42a is equal to or higher than a predetermined threshold value. This threshold can be set to 0 ° C., for example, but can be changed as appropriate. Then, the end determination unit 24 determines that the temperature of the refrigerant is equal to or higher than the threshold value while the first sub heat exchange unit 41 or the second sub heat exchange unit 42 is defrosted. In this case, it is determined that the defrosting of the first sub heat exchange unit 41 or the second sub heat exchange unit 42 has been completed.
  • the refrigerant is the compressor 2, the pressure switching unit 3, the second heat exchanger 7, the expansion device 6, the inflow switching unit 5, the first heat exchange unit 4, the inflow switching unit 5, the pressure feeding switching unit 3, It distributes in order of the compressor 2.
  • both the first sub heat exchange unit 41 and the second sub heat exchange unit 42 only absorb heat from the outdoor air 11.
  • the refrigerant may flow into the auxiliary heat exchange unit 41 first, or the refrigerant may flow into the second auxiliary heat exchange unit 42 first.
  • bypass valve 62 is closed to sufficiently expand the refrigerant by the expansion device 6. Note that the pressure loss in the first heat exchange unit 4 is reduced as much as possible by fully opening the sub expansion device 43 and opening the sub bypass valve 45, or both of them. Note that the opening degree of the sub-expansion device 43 may not be fully opened.
  • the high-temperature refrigerant discharged from the compressor 2 exchanges heat with the indoor air 12 in the second heat exchanger 7 to be dissipated to heat the room.
  • the refrigerant liquefied at a low temperature is expanded by the expansion device 6 to be low-pressure to be gas-liquid two-phase.
  • the refrigerant absorbs heat from the outdoor air 11 in the first heat exchange unit 4 and is vaporized, and is sucked into the compressor 2 to be increased in temperature and pressure again.
  • the heat pump device 1 can continuously heat the room.
  • the refrigerant may flow into the first auxiliary heat exchange unit 41 from the inflow switching unit 5 or the refrigerant flows into the second auxiliary heat exchange unit 42 first. Also good. Further, the bypass valve 62 is closed to sufficiently expand the refrigerant by the expansion device 6. Note that the pressure loss in the first heat exchange unit 4 is reduced as much as possible by fully opening the sub expansion device 43 and opening the sub bypass valve 45, or both of them. Note that the opening degree of the sub-expansion device 43 may not be fully opened.
  • the high-temperature refrigerant discharged from the compressor 2 is radiated by exchanging heat with the outdoor air 11 in the first heat exchange unit 4.
  • the refrigerant liquefied at a low temperature is expanded by the expansion device 6 to be low-pressure to be gas-liquid two-phase.
  • the refrigerant absorbs heat from the indoor air 12 in the second heat exchanger 7 to cool the room.
  • the refrigerant that has absorbed heat and is vaporized is sucked into the compressor 2 and is again heated to high temperature and pressure.
  • the heat pump device 1 can continuously cool the room.
  • the normal heating operation and the normal cooling operation are mainly performed.
  • the heat contained in the outdoor air 11 is exchanged between the low-temperature refrigerant and the outdoor air 11, so that the moisture contained in the outdoor air 11 is changed to the outer surface of the first heat exchange unit 4. It adheres to and becomes frost.
  • the heat resistance increases, and the heat exchange efficiency of the first heat exchange unit 4 decreases.
  • frost adhesion is left unattended, the air passage is filled with frost, and eventually the air passage is blocked. Thereby, the outdoor air 11 is not circulated, and heat exchange in the first heat exchange unit 4 may be impossible. In order to avoid such a situation, a defrosting operation is required.
  • High temperature defrosting operation As the defrosting operation, a high temperature defrosting operation (also referred to as hot gas defrosting operation) will be described.
  • the refrigerant flow direction is the same as in the normal cooling operation. That is, the high-temperature refrigerant discharged from the compressor 2 flows into the first heat exchange unit 4. Thereby, the frost adhering to the 1st heat exchange unit 4 is melted by the high temperature refrigerant
  • heat used for defrosting at the time of the high temperature defrosting operation escapes to the outdoor air 11 having a low temperature at the time of the normal heating operation. Is stopped to suppress Such a high-temperature defrosting operation is one of the most commonly performed defrosting methods in a heat pump device.
  • the heat pump device 1 ensures comfort by enabling execution of the defrost heating operation and the semi-high temperature defrost operation in addition to the high temperature defrost operation.
  • defrosting heating operation that is, while defrosting one of the first auxiliary heat exchanging part 41 and the second auxiliary heat exchanging part 42, the other heat is absorbed and the second heat exchanger 7 dissipates heat.
  • operation to perform is demonstrated.
  • the refrigerant is the compressor 2, the pressure switching unit 3, the second heat exchanger 7, the bypass circuit 61 and the expansion device 6, the inflow switching unit 5, the first sub heat exchange unit 41, the sub expansion device 43, The second auxiliary heat exchange unit 42, the inflow switching unit 5, the pumping switching unit 3, and the compressor 2 are distributed in this order.
  • the defrosting control means 22 in the control unit 21 opens the bypass valve 62, reduces the amount of refrigerant flowing through the expansion device 6, opens the expansion device 6 fully open, and expands the refrigerant in the expansion device 6. Suppress.
  • the bypass valve 62 is opened, the refrigerant pressure difference before and after the expansion device 6 disappears, so that expansion of the refrigerant is suppressed without fully opening the expansion device 6.
  • the opening degree of the expansion device 6 is fully opened. Then, the defrosting control means 22 in the control unit 21 closes the sub-bypass valve 45 and increases the amount of refrigerant flowing through the sub-expansion device 43 to promote expansion of the refrigerant in the sub-expansion device 43.
  • the high-temperature refrigerant discharged from the compressor 2 exchanges heat with the indoor air 12 in the second heat exchanger 7 to be dissipated to heat the room.
  • the refrigerant having a low temperature by heating the room has at least the temperature of the indoor air 12, that is, a temperature sufficient for defrosting, even if the maximum heat exchange is performed in the second heat exchanger 7.
  • it since it is not expanded too much in the expansion device 6, it can distribute
  • the control unit 21 detects that the temperature of the refrigerant that has flowed out of the first auxiliary heat exchange unit 41 (the temperature detected by the first temperature detection unit 41a and is close to the condensation temperature of the refrigerant) is that the frost has melted.
  • the opening degree of the sub-expansion device 43 is adjusted to be slightly higher than the temperature at which the sub-expansion device is set, for example, 1 ° C.
  • the opening degree of the sub expansion device 43 is increased, the condensation temperature of the refrigerant decreases, and when the opening degree of the sub expansion device 43 is decreased, the condensation temperature of the refrigerant increases.
  • the control unit 21 determines that the temperature of the refrigerant flowing out from the second heat exchanger 7 (detected by the temperature detection unit 9) You may make it adjust the opening degree of the subexpansion apparatus 43 so that predetermined temperature difference (for example, 4 degreeC) may become higher than temperature.
  • predetermined temperature difference for example, 4 degreeC
  • the control unit 21 adjusts the opening degree of the sub-expansion device 43 so that the temperature of the refrigerant discharged from the compressor 2 (detected by the temperature detection unit 13) becomes the set discharge temperature. You may do it.
  • the opening degree of the sub expansion device 43 is increased, the discharge temperature of the refrigerant is lowered, and when the opening degree of the sub expansion device 43 is lowered, the discharge temperature of the refrigerant is raised.
  • the set discharge temperature is, for example, the temperature of the refrigerant that has flowed out of the first auxiliary heat exchange unit 41 (the temperature detected by the first temperature detection unit 41a and close to the condensation temperature of the refrigerant), and the secondary expansion.
  • the temperature of the refrigerant that expands in the device 43 and flows into the second auxiliary heat exchange unit 42 (the temperature detected by the second temperature detection unit 42a and close to the evaporation temperature of the refrigerant), the frequency of the compressor 2 and It is a value calculated using structural characteristics (such as the volume of the portion to be compressed) and refrigerant characteristics (such as the type of refrigerant, the set degree of superheat or the set degree of cooling). Note that if the lower limit value of the calculated set discharge temperature is set to be at least a predetermined temperature (for example, 5 ° C.) higher than the temperature of the indoor air 12, the refrigerant discharge temperature is excessively lowered and heating is performed. It is possible to avoid such a situation that it becomes impossible.
  • a predetermined temperature for example, 5 ° C.
  • the method for determining the opening degree of the sub-expansion device 43 is not so-called feedback control in which the opening degree of the sub-expansion device 43 is appropriately changed based on the detected refrigerant discharge temperature or condensation temperature.
  • so-called feedforward control may be used in which the opening degree of the sub-expansion device 43 is uniquely determined by a plurality of patterns determined in advance according to the frequency of the compressor 2 and the temperature of the outdoor air 11. Then, the refrigerant which has been expanded in the auxiliary expansion device 43 and reduced in pressure and gas-liquid two-phased is absorbed by the second auxiliary heat exchanging part 42 from the outdoor air 11 and vaporized, and is sucked into the compressor 2 to be again heated and pressurized again. It becomes.
  • the heat pump device 1 absorbs heat at the second sub heat exchange unit 42 and radiates heat at the second heat exchanger 7 while defrosting the first sub heat exchange unit 41, Can be continuously heated.
  • this defrosting heating operation although the maximum capacity in the normal heating operation in which heat is absorbed by both the first auxiliary heat exchanging part 41 and the second auxiliary heat exchanging part 42 is not reached, the indoor temperature can be raised to some extent. For example, the need for heating at maximum capacity is low and comfort is not impaired.
  • a semi-high temperature defrosting operation (also referred to as a semi-hot gas defrosting operation), that is, while defrosting one of the first auxiliary heat exchanging part 41 and the second auxiliary heat exchanging part 42, The operation of absorbing heat and absorbing heat in the second heat exchanger 7 will be described.
  • the refrigerant is the compressor 2, the pressure switching unit 3, the inflow switching unit 5, the first sub heat exchange unit 41, the sub expansion device 43, the second sub heat exchange unit 42, the inflow switching unit 5, and the bypass circuit. 61, the expansion device 6, the second heat exchanger 7, the pumping switching unit 3, and the compressor 2 are distributed in this order.
  • the defrosting control means 22 in the control unit 21 opens the bypass valve 62, reduces the amount of refrigerant flowing through the expansion device 6, opens the expansion device 6 fully open, and expands the refrigerant in the expansion device 6. Suppress.
  • the bypass valve 62 is opened, the refrigerant pressure difference before and after the expansion device 6 disappears, so that expansion of the refrigerant is suppressed without fully opening the expansion device 6.
  • the opening degree of the expansion device 6 is fully opened.
  • the defrosting control means 22 in the control unit 21 closes the sub-bypass valve 45 and increases the amount of refrigerant flowing through the sub-expansion device 43 to promote expansion of the refrigerant in the sub-expansion device 43.
  • the controller 21 causes the temperature of the refrigerant flowing out from the first auxiliary heat exchanging unit 41 (the temperature detected by the first temperature detecting unit 41a, which is close to the refrigerant condensing temperature) to melt the frost.
  • the opening degree of the sub expansion device 43 is adjusted so as to be higher than the temperature, for example, 2 ° C.
  • the opening degree of the sub expansion device 43 is increased, the condensation temperature of the refrigerant decreases, and when the opening degree of the sub expansion device 43 is decreased, the condensation temperature of the refrigerant increases.
  • the control unit 21 adjusts the opening degree of the sub-expansion device 43 so that the temperature of the refrigerant discharged from the compressor 2 (detected by the temperature detection unit 13) becomes the set discharge temperature. You may do it.
  • the opening degree of the sub expansion device 43 is increased, the discharge temperature of the refrigerant is lowered, and when the opening degree of the sub expansion device 43 is lowered, the discharge temperature of the refrigerant is raised.
  • the set discharge temperature is, for example, the temperature of the refrigerant that has flowed out of the first auxiliary heat exchange unit 41 (the temperature detected by the first temperature detection unit 41a and close to the condensation temperature of the refrigerant), and the secondary expansion.
  • the temperature of the refrigerant that expands in the device 43 and flows into the second auxiliary heat exchange unit 42 is a value calculated using structural characteristics (such as the volume of the portion to be compressed) and refrigerant characteristics (such as the type of refrigerant, the set degree of superheat or the set degree of cooling).
  • the method for determining the opening degree of the sub-expansion device 43 is not so-called feedback control in which the opening degree of the sub-expansion device 43 is appropriately changed based on the detected refrigerant discharge temperature or condensing temperature as described above.
  • a so-called feed-forward control may be employed in which the opening degree of the sub-expansion device 43 is uniquely determined by a plurality of patterns determined in advance according to the frequency of the machine 2 and the temperature of the outdoor air 11.
  • the high-temperature refrigerant discharged from the compressor 2 flows into the first sub heat exchange unit 41, and the frost adhering to the first sub heat exchange unit 41 is melted by the high-temperature refrigerant and removed. Frosted.
  • the refrigerant that has been expanded in the sub-expansion device 43 and reduced in pressure to be gas-liquid two-phase is vaporized by absorbing heat from the outdoor air 11 in the second sub-heat exchanger 42. Since the vaporized refrigerant is not expanded by the expansion device 6, it remains at a high temperature (although it is at most about the same temperature as the outdoor air 11, which is a heat source), and the outdoor air 11 is cooler than the indoor air 12.
  • the semi-high temperature defrosting operation unlike the defrosting heating operation, heating is not continued while defrosting, but most of the heat source necessary for defrosting is the second auxiliary heat exchange unit 42. It is covered by outdoor air 11.
  • the second auxiliary heat exchanging unit 42 is also defrosted, so the heat source necessary for defrosting is the indoor air 12 in the second heat exchanger 7. Therefore, in the semi-high temperature defrosting operation, the heat absorption from the indoor air 12 in the second heat exchanger 7 is suppressed more than in the high temperature defrosting operation.
  • the semi-high temperature defrosting operation is performed, the temperature of the indoor air 12 is suppressed from excessively decreasing, and thus comfortable. Does not impair sex.
  • both the defrosting heating operation and the semi-high temperature defrosting operation may be appropriately changed by the control unit 21. For example, when the room is not sufficiently warm and the room temperature is low, the defrost heating operation is performed and the heating is continued. In addition, when the room is sufficiently warm and the room temperature is high, a semi-high temperature defrosting operation is performed to increase the defrosting capacity and to defrost in a shorter time so that the normal heating operation can be quickly restored. .
  • the semi-high temperature defrosting operation when the room is not sufficiently warm, the semi-high temperature defrosting operation may be performed, and when the room is sufficiently warm, the defrosting heating operation may be performed. In this way, by properly using the defrosting heating operation and the semi-high temperature defrosting operation, it is possible to appropriately select whether to give priority to indoor comfort or to defrost efficiency.
  • the control unit 21 determines the end of the defrosting. Specifically, the threshold determination unit 23 determines whether or not the temperature of the refrigerant detected by the first temperature detection unit 41a or the second temperature detection unit 42a is equal to or higher than a predetermined threshold, When the threshold determination unit 23 determines that the temperature of the refrigerant is equal to or higher than the threshold while the end determination unit 24 defrosts the first sub heat exchange unit 41 or the second sub heat exchange unit 42. It is determined that the defrosting of the auxiliary heat exchange unit has been completed.
  • This determination uses an action in which the temperature of the refrigerant starts to rise rapidly because the heat absorption source disappears when the defrosting in the auxiliary heat exchange unit is completed.
  • the opening degree of the sub-expansion device 43 is controlled according to the condensation temperature, the temperature rise of the refrigerant as described above is suppressed by controlling the opening degree of the sub-expansion device 43. For this reason, you may make it determine with the defrosting having been complete
  • the defrosting end determination in the high temperature defrosting operation is performed using the temperature detection unit 10 provided between the first heat exchange unit 4 and the expansion device 6, and the refrigerant flowing out from the first heat exchange unit 4.
  • the predetermined threshold value is set to a temperature (for example, 3 ° C.) slightly higher than 0 ° C. as a temperature at which frost melts. This is because the temperature of the refrigerant does not become higher than the temperature at which the frost melts due to the heat of melting of the frost unless the defrosting of the auxiliary heat exchange unit is completed, and the temperature is slightly higher. This is because it takes into account the increase in the thermal resistance between the refrigerant and the frost and the change in the melting temperature of the frost due to the atmospheric pressure of the outdoor air 11.
  • the first heat exchange unit 4 installed outdoors has the first sub heat exchange unit 41, the second sub heat exchange unit 42, and the sub heat exchange unit 42.
  • the expansion device 43 is configured.
  • the defrosting control means 22 defrosts the first sub heat exchange section 41 or the second sub heat exchange section 42
  • the pressure difference of the refrigerant flowing through the first heat exchange unit 4 is sub-expanded. Increase with device 43.
  • the heat pump apparatus 1 thermally radiates, and it absorbs heat from the other simultaneously.
  • the 2nd heat exchanger 7 installed indoors by absorbing heat from the other.
  • warm heat can be supplied to the indoor air 12 (defrost heating operation).
  • the quantity absorbed by the 2nd heat exchanger 7 is absorbed by absorbing heat from the other. It can be reduced (semi-high temperature defrosting operation).
  • the defrosting can be performed while the heat is supplied to the room which is the heat demand section, so that the user's discomfort is suppressed and the comfort is improved.
  • the refrigerant discharged from the compressor 2 is supplied to the second heat exchanger 7 (load heat exchanger) before the first heat exchange unit 4.
  • the first sub heat exchange unit 41 or the second sub heat exchange unit 42 is defrosted using the residual heat of the refrigerant radiated by the second heat exchanger 7. . For this reason, energy efficiency is high.
  • the high-temperature refrigerant discharged from the compressor 2 is supplied to the first heat exchange unit 4 before the second heat exchanger 7. Although energy efficiency is not so high, it is possible to defrost at high speed.
  • the defrosting heating operation and the semi-high temperature defrosting operation are realized. Therefore, the distribution route is simple, and the size and cost of the device increase with the increase in the number of devices. The rise can be suppressed. Further, the refrigerant flow path is the same in the normal heating operation and the defrosting heating operation, and is the same in the normal cooling operation and the semi-high temperature defrosting operation. For this reason, an unnecessary valve required for switching the operation mode can be omitted, and the number of portions where the refrigerant pool is generated can be reduced.
  • the refrigerant pool does not occur before and after the defrosting process, the process for eliminating the refrigerant pool is unnecessary, and the operation of the heat pump device 1 is simple. Thereby, it is allowed to lower the pressure resistance performance of the pipe, and an increase in the amount of the refrigerant can be suppressed, so that an increase in cost can be suppressed.
  • the pressure feed switching unit 3 since the pressure feed switching unit 3 is provided, the flow direction of the refrigerant can be changed by the pressure feed switching unit 3. For this reason, both normal heating operation for supplying warm air to the indoor air 12 and normal cooling operation for supplying cold heat to the indoor air 12 are possible.
  • the refrigerant discharged from the compressor 2 is supplied to the second heat exchanger 7 (load heat exchanger) prior to the first heat exchange unit 4, and the second heat exchanger 7 Defrosting heating operation for defrosting the first auxiliary heat exchanging part 41 or the second auxiliary heat exchanging part 42 in the first heat exchanging unit 4 using the residual heat of the radiated refrigerant, and compression
  • the high-temperature refrigerant discharged from the machine 2 is supplied to the first heat exchange unit 4 before the second heat exchanger 7, and the first sub heat exchange in the first heat exchange unit 4 is performed.
  • the high temperature defrosting operation and the semi-high temperature defrosting operation in which the part 41 or the second auxiliary heat exchange unit 42 is directly defrosted with a high temperature refrigerant can be used properly.
  • the inflow switching unit 5 can change the flow direction of the refrigerant in the first heat exchange unit 4.
  • the defrosting control means 22 increases the pressure difference of the sub expansion device 43 while switching the refrigerant flow direction in the inflow switching unit 5, whereby the first sub heat exchange unit 41 and the second sub heat.
  • heat can be removed and defrosted to the auxiliary heat exchange part through which the refrigerant flows first, and then absorbed by the auxiliary heat exchange part through which the refrigerant flows.
  • the defrosting heating operation and the semi-high temperature defrosting operation are performed by the first sub heat exchange unit 41 and the second sub heat exchange. This can be done in part 42.
  • bypass circuit 61 and the bypass valve 62 are provided, the operation of closing the bypass valve 62 and increasing the refrigerant pressure difference before and after the expansion device 6, that is, normal heating operation, normal cooling operation, and An operation in which the high-temperature defrosting operation is possible and the bypass valve 62 is opened to reduce the refrigerant pressure difference before and after the expansion device 6 and increase the refrigerant pressure difference before and after the auxiliary expansion device 43, that is, Defrosting heating operation and semi-high temperature defrosting operation are possible. For this reason, the energy efficiency at the time of defrosting improves.
  • auxiliary bypass circuit 44 and the auxiliary bypass valve 45 are provided, the operation of closing the auxiliary bypass valve 45 and increasing the refrigerant pressure difference before and after the auxiliary expansion device 43, that is, the defrosting heating operation.
  • the semi-high temperature defrosting operation is possible, and by opening the auxiliary bypass valve 45 and bypassing the auxiliary expansion device 43, the pressure difference of the refrigerant before and after the auxiliary expansion device 43 is reduced, and the first auxiliary defrosting operation is performed.
  • An operation that absorbs or dissipates heat from both the heat exchange unit 41 and the second auxiliary heat exchange unit 42, that is, a normal heating operation, a normal cooling operation, and a high-temperature defrosting operation are possible. Thereby, the increase in the pressure loss in the 1st heat exchange unit 4 can be suppressed, and the fall of efficiency can be suppressed.
  • coolant with an opening degree is employ
  • the determination accuracy of the completion of the defrosting in the defrosting heating operation and the semi-high temperature defrosting operation is extremely high. For this reason, useless energy consumption required for defrosting can be suppressed. Moreover, the defrosting time can be suppressed, and the effect of improving comfort or reducing discomfort is further enhanced.
  • a heat pump device 1 according to a modification of the first embodiment will be described.
  • the heat pump device 1 can perform the normal heating operation and the defrosting heating operation even if the pumping switching unit 3 is omitted.
  • the normal cooling operation, the high temperature defrosting operation, and the semi-high temperature defrosting operation are possible even if the pumping switching unit 3 is omitted.
  • the pumping switching part 3 can be omitted.
  • the inflow switching unit 5 can be omitted.
  • frost is likely to be generated in one of the first sub heat exchange unit 41 and the second sub heat exchange unit 42 (for example, frost formation on the sub heat exchange unit on the upstream side with respect to the flow of the outdoor air 11).
  • frost is likely to be generated in one of the first sub heat exchange unit 41 and the second sub heat exchange unit 42 (for example, frost formation on the sub heat exchange unit on the upstream side with respect to the flow of the outdoor air 11).
  • frost is likely to be generated in one of the first sub heat exchange unit 41 and the second sub heat exchange unit 42 (for example, frost formation on the sub heat exchange unit on the upstream side with respect to the flow of the outdoor air 11).
  • frost is likely to be generated in one of the first sub heat exchange unit 41 and the second sub heat exchange unit 42 (for example, frost formation on the sub heat exchange unit on the upstream side with respect to the flow of the outdoor air 11).
  • one of them can be defrosted at a high speed by a
  • either the first sub heat exchange unit 41 or the second sub heat exchange unit 42 is defrosted while being heated by the defrost heating operation, and both are simultaneously defrosted at a high speed by the high temperature defrost operation. You may do it. Thereby, even if it omits the inflow switching part 5, when it is at least a semi-high temperature defrost operation or a defrost heating operation, the fall of comfort can be suppressed.
  • the bypass circuit 61 and the bypass valve 62 can be omitted as long as the pressure loss is in an allowable range. This contributes to cost reduction.
  • the sub bypass circuit 44 and the sub bypass valve 45 can be omitted as long as the pressure loss is within an allowable range.
  • the sub-expansion device 43 may be configured by a capillary tube instead of the expansion valve that adjusts the refrigerant flow rate.
  • This capillary tube does not change the opening degree like an expansion valve, and the pressure difference before and after passage is fixed in accordance with the circulation amount of the refrigerant.
  • the present invention is not limited to this. It is good also as a structure to cool.
  • the liquid heated or cooled by the second heat exchanger 7 may be used to indirectly heat or cool the room with a fan coil, radiator, floor heating, or the like disposed in the room. Good.
  • the heat demand unit may generate hot water, hot water for heating, cold water for cooling, or the like.
  • the bypass valve 62 and the sub bypass valve 45 have been described as on-off valves that adjust whether the refrigerant flows or stops in the bypass circuit 61 and the sub bypass circuit 44. It is preferable to use a valve that gradually changes (for example, 2 minutes are required for opening and closing) including an intermediate opening between the closed state and the fully opened state. In this case, when various operation modes (normal heating operation, defrost heating operation, high temperature defrost operation, semi-high temperature defrost operation, etc.) are switched, the temperature, pressure or amount of the refrigerant in each part of the refrigerant circuit 8 is rapidly changed. Smooth switching is possible while suppressing various fluctuations.
  • various operation modes normal heating operation, defrost heating operation, high temperature defrost operation, semi-high temperature defrost operation, etc.
  • finish judgment of the defrost in a defrost heating operation, a semi-high temperature defrost operation, or a high temperature defrost operation is made into the 1st temperature detection part 41a, the 2nd temperature detection part 42a, or temperature detection.
  • the absolute value comparison of the temperature detected in the unit 10 is performed, the relative value comparison by the temperature change at a predetermined time interval, or both the absolute value comparison and the relative value comparison may be performed. In this case, the same effect as that of the first embodiment is obtained.
  • the heat pump apparatus 1 is provided with the suppression means which suppresses heat exchange with the exterior of the sub bypass valve 45, and air.
  • the suppression means can be realized, for example, by laying a heat insulating material on the outside of the sub bypass valve 45, or by forming a two-layer structure outside the movable part of the sub bypass valve 45 and enclosing a dry gas between the layers.
  • the suppression means is arranged at a location away from the auxiliary heat exchange part so that it does not come in contact with moisture, or a shielding part is provided between the auxiliary heat exchange part so that the air containing moisture is difficult to hit. It can be realized by doing. Thereby, the frost formation to the sub bypass valve 45 can be suppressed, and the malfunction of the operation
  • the heat pump device 1 may include a heating unit such as a heater in the sub bypass valve 45 instead of the suppression means.
  • a heating unit such as a heater in the sub bypass valve 45 instead of the suppression means.
  • the control unit 21 determines that it is necessary to operate the sub bypass valve 45 after a normal heating operation or the like.
  • the sub bypass valve 45 is heated by the heating unit and defrosted, whereby ice accretion is achieved.
  • the sub bypass valve 45 can be operated reliably.
  • the heat pump device 1 may include both the suppression unit and the heating unit. In this case, heat radiation from the heating unit to the outside can be suppressed, and the outside of the sub bypass valve 45 can be efficiently defrosted.
  • FIG. 2 is a schematic diagram showing a heat pump device 100 according to the second embodiment.
  • the second embodiment is different from the first embodiment in that a plurality of flow paths through which the refrigerant branches and flows are formed in the first sub heat exchange section 41 and the second sub heat exchange section 42. Is different.
  • portions common to the first embodiment are denoted by the same reference numerals, description thereof is omitted, and differences from the first embodiment will be mainly described.
  • a first circulation path 4 a and a second circulation path 4 b are formed in the first auxiliary heat exchanging part 41 so that the refrigerant always branches and flows in parallel.
  • the first distribution path 4a and the second distribution path 4b are also formed in the second auxiliary heat exchange unit 42 as they are.
  • the first flow path 4a branches between the first sub heat exchange unit 41 and the second sub heat exchange unit 42, one is connected to one end of the sub expansion device 43, and the other is the first It is connected to one end of the sub bypass circuit 44a.
  • the first flow path 4a joins again at the other end of the sub-expansion device 43 and the other end of the first sub-bypass circuit 44a.
  • the first sub bypass circuit 44a is provided with a first sub bypass valve 45a.
  • the first sub bypass valve 45a controls whether or not the refrigerant flows through the first sub bypass circuit 44a.
  • the second flow path 4b also branches between the first sub heat exchange unit 41 and the second sub heat exchange unit 42, one of which is connected to one end of the sub expansion device 43, and the other is the second sub heat exchange unit 42. 2 is connected to one end of the secondary bypass circuit 44b. Then, the second flow path 4b joins again at the other end of the sub expansion device 43 and the other end of the second sub bypass circuit 44b.
  • the second sub bypass circuit 44b is provided with a second sub bypass valve 45b.
  • the second sub bypass valve 45b controls whether or not the refrigerant flows through the second sub bypass circuit 44b.
  • the secondary expansion device 43 is installed at a portion where the first distribution path 4a and the second distribution path 4b merge.
  • the first temperature detection unit 41a and the second temperature detection unit 42a are provided at both ends of the sub-expansion device 43 installed at the portion where the first flow path 4a and the second flow path 4b merge. It has been.
  • the heat pump device 100 according to the second embodiment is different from the first embodiment in that a plurality of distribution paths are formed, but a normal heating operation, a normal cooling operation, a defrost heating operation, and a semi-high temperature defrost operation.
  • the operation of the high temperature defrosting operation is the same as that of the first embodiment.
  • the first sub-bypass valve 45a and the second sub-bypass valve 45b in the second embodiment are simultaneously opened and closed at the same timing when the sub-bypass valve 45 in the first embodiment is opened and closed.
  • the configuration adopted in the modification of the first embodiment can also be adopted in the second embodiment.
  • the first flow path 4a and the second flow path through which the refrigerant branches and flows to the first sub heat exchange unit 41 and the second sub heat exchange unit 42 Since 4b is formed, the pressure loss in the 1st sub heat exchange part 41 and the 2nd sub heat exchange part 42 is reduced more. For this reason, in addition to the effect obtained in the first embodiment, the efficiency of the refrigeration cycle in the refrigerant circuit 8 can be increased.
  • first secondary bypass circuit 44a and the second secondary bypass circuit 44b are connected to the first circulation path 4a and the second circulation path 4b, respectively, bypass for bypassing the secondary expansion device 43
  • the function is improved and the pressure difference of the refrigerant is reduced.
  • the first circulation path 4a and the second circulation path are formed at both ends of the sub-expansion device 43. Since the two distribution channels 4b once join, this imbalance is corrected naturally. At that time, the first distribution path 4a and the second distribution path 4b are merged after branching to the first sub-bypass circuit 44a and the second sub-bypass circuit 44b, respectively. There is no increase in pressure loss, or a large increase.
  • the first sub bypass valve 45a and the second sub bypass valve 45b are provided separately for the first sub bypass circuit 44a and the second sub bypass circuit 44b, respectively.
  • it is a body valve, it is opened and closed simultaneously at the same timing, and even if the valve body is formed integrally or a single motor that supplies the driving power required for opening and closing is combined Good. In this case, it becomes easier to obtain the effect of downsizing or cost reduction.
  • first sub-bypass circuits 44a and first sub-bypass valves 45a may be provided in the first distribution path 4a.
  • a plurality of second sub-bypass circuits 44b and second sub-bypass valves 45b may be provided in the second flow path 4b.
  • the same number of flow paths (the first flow path 4a and the second flow path) are used in the first sub heat exchange unit 41 and the second sub heat exchange unit 42 before and after the sub expansion device 43.
  • a different number of distribution channels may be used.
  • a plurality of secondary bypass circuits are branched from at least one distribution path.
  • FIG. 3 is a schematic diagram showing a heat pump device 200 according to the third embodiment.
  • the third embodiment is different from the first embodiment in that the heat exchange unit 4 includes a plurality of, for example, first heat exchange units 4-1 and 4-2.
  • portions common to the first embodiment are denoted by the same reference numerals, description thereof is omitted, and differences from the first embodiment will be mainly described.
  • the third embodiment includes two first heat exchange units 4-1 and 4-2, and the refrigerant flows from the inflow switching unit 5 to the refrigerant forward piping and the return passage.
  • the first heat exchange units 4-1 and 4-2 are branched in parallel, and then merged.
  • the first heat exchange unit 4-1 includes a first sub heat exchange unit 41-1, a second sub heat exchange unit 42-1, a first temperature detection unit 41a-1, and a second temperature detection unit 42a. -1, a secondary expansion device 43-1, a secondary bypass circuit 44-1, and a secondary bypass valve 45-1.
  • the second heat exchange unit 4-2 includes a first sub heat exchange unit 41-2, a second sub heat exchange unit 42-2, a first temperature detection unit 41a-2, and a second temperature detection.
  • a portion 42a-2, a sub expansion device 43-2, a sub bypass circuit 44-2, and a sub bypass valve 45-2 are provided.
  • the first heat exchange unit 4-1 and the second heat exchange unit 4-2 have the same configuration.
  • the refrigerant flowing from the inflow switching unit 5 always branches in parallel to the first heat exchange units 4-1, 4-2 and flows into the first heat exchange units 4-1, 4-2.
  • the refrigerant discharged from the heat exchange units 4-1 and 4-2 joins and returns to the inflow switching unit 5. Therefore, as in the first embodiment, in each of the first heat exchange units 4-1 and 4-2, the refrigerant flow is always the same as in the first embodiment regardless of the operating state. In series.
  • the first auxiliary heat exchange units 41-1 and 41-2 are defrosted at the same time, or the second auxiliary heat exchange units 42-1 and 42- The operation of either defrosting 2 at the same time is performed.
  • the sub bypass valves 45-1 and 45-2 are simultaneously closed, and the control unit 21 performs the same method as in the first embodiment in accordance with the discharge temperature (temperature detected by the temperature detection unit 13).
  • the sub-expansion devices 43-1 and 43-2 are set to the same opening degree.
  • the opening degree of the sub expansion device 43-1 is determined by the first temperature detection unit.
  • 41a-1 is controlled according to the temperature (close to the condensing temperature, more precisely, the temperature obtained by subtracting the subcooling temperature from the condensing temperature), and the opening degree of the sub expansion device 43-2 is determined by the first temperature detecting unit.
  • the temperature may be controlled according to the temperature detected at 41a-2 (close to the condensation temperature, more precisely, the temperature obtained by subtracting the subcool temperature from the condensation temperature).
  • the opening degree of the sub expansion devices 43-1 and 43-2 depends on the temperature of the first temperature detection units 41a-1 and 41a-2 (or the second temperature detection units 42a-1 and 42a-2).
  • the opening ratio of the sub-expansion devices 43-1 and 43-2 is maintained at a controlled value according to the discharge temperature (the temperature detected by the temperature detector 13).
  • the discharge temperature and the temperature close to the condensation temperature may be controlled simultaneously by increasing / decreasing itself. Then, when the detection values of the first temperature detection units 41a-1 and 41a-2 are both higher than a predetermined value, it is determined that the defrosting is finished.
  • the third embodiment has a configuration in which a plurality of first heat exchange units 4-1 and 4-2 are arranged in parallel, and performs the same operation as in the first embodiment.
  • the pressure loss of the refrigerant circuit 8 on the first heat exchange units 4-1 and 4-2 side is further suppressed.
  • FIG. 4 is a schematic diagram showing the first heat exchange unit 4 in the fourth embodiment.
  • the heat pump device 300 includes the blower fan 46, and the blower fan 46 is provided individually for each of the plurality of sub heat exchange units in the first heat exchange unit 4. This is different from the first embodiment.
  • portions common to the first embodiment are denoted by the same reference numerals, description thereof is omitted, and differences from the first embodiment will be mainly described.
  • the first sub heat exchange unit 41 and the second sub heat exchange unit 42 in the first heat exchange unit 4 are individually connected to the first heat exchange unit 41.
  • a first blower fan 46a and a second blower fan 46b are provided.
  • a partition plate 47 is provided between the first sub heat exchange unit 41 and the second sub heat exchange unit 42, and this partition plate 47 is blown by the first blower fan 46a.
  • the outdoor air 11a and the outdoor air 11b blown by the second blower fan 46b are separated.
  • the control unit 21 performs defrosting.
  • the blower fan on the side of the heat exchange unit is stopped, and the blower fan on the side of the auxiliary heat exchange unit that is not defrosted is operated to continue the heat absorption operation.
  • the rotation of the first blower fan 46a is stopped and the outdoor air 11a is changed to the first sub heat exchange unit 42.
  • the second blower fan 46 b While not being supplied to the heat exchanging part 41, the second blower fan 46 b is rotated, and the outdoor air 11 b is supplied to the second auxiliary heat exchanging part 42. Thereby, since it becomes difficult to radiate heat to the outdoor air 11a in the first sub heat exchange part 41, it is possible to efficiently defrost, and the second sub heat exchange part 42 efficiently absorbs heat from the outdoor air 11b. be able to.
  • the control unit 21 stops the rotation of both the first blower fan 46a and the second blower fan 46b, and efficiently suppresses heat radiation from the refrigerant to the outdoor air 11. Defrosted.
  • the control unit 21 rotates both the first blower fan 46a and the second blower fan 46b, and the first heat exchange unit 4 performs the normal heating operation. Heat can be absorbed from the outdoor air 11 efficiently, and heat can be efficiently radiated to the outdoor air 11 in the normal cooling operation.
  • the partition plate 47 is provided, but the partition plate 47 may be omitted. Further, when the fourth embodiment and the third embodiment are combined, one blower fan corresponding to the first sub heat exchange units 41-1 and 41-2 is provided, and the second sub heat exchange unit 42 is provided. -1 and 42-2 may be provided with another blower fan.
  • FIG. 5 is a schematic diagram showing the first heat exchange unit 4 in the fifth embodiment.
  • the heat pump device 400 includes the blower fan 46, and the blower fan 46 is different from the first embodiment in that the air blowing direction can be switched in both directions.
  • portions common to the first embodiment are denoted by the same reference numerals, description thereof is omitted, and differences from the first embodiment will be mainly described.
  • the blowing fan 46 switches the direction of blowing the outdoor air 11 in both directions by changing the rotation direction.
  • a direction in which the air is blown from the auxiliary heat exchange unit to the blower fan 46 is a forward direction 11c
  • a direction in which the air is blown from the blower fan 46 to the auxiliary heat exchange unit is a reverse direction 11d.
  • the first sub heat exchange part 41 and the second sub heat exchange part 42 are arranged in series with respect to the air blowing direction of the air blown by the blower fan 46.
  • the control unit The defrosting control means 22 in 21 changes the air blowing direction in the blower fan 46 so that the defrosting side auxiliary heat exchanging part is located upstream of the air blowing direction in the blower fan 46. Switch.
  • the defrosting control means 22 determines the blowing direction of the outdoor air 11 by the blower fan 46, Switch to the forward direction 11c.
  • the defrosting control unit 22 determines the blowing direction of the outdoor air 11 by the blower fan 46. Switch to the reverse direction 11d.
  • the rotational speed of the blower fan 46 is set lower than that in the normal heating operation or the normal cooling operation so that the heat released from the refrigerant during the defrosting is not excessively taken away by the outdoor air 11. It is preferable to make it.
  • the blower fan 46 is stopped in order to efficiently defrost.
  • the heat released from the refrigerant in the upstream side secondary heat exchange unit for defrosting is recovered as a heat absorption source in the downstream side secondary heat exchange unit that continues the endothermic operation. For this reason, it is possible to achieve efficient defrosting and heat absorption only by providing one blower fan 46, and to reduce the number of parts, and to manufacture a heat pump device 400 with low cost, compactness, low failure risk, and high reliability. Can do.
  • the first auxiliary heat exchanging units 41-1 and 41-2 are arranged in parallel upstream or downstream with respect to the blowing direction in the blower fan 46.
  • the second auxiliary heat exchange units 42-1 and 42-2 are arranged in parallel on the downstream side or the upstream side with respect to the blowing direction in the blower fan 46, and the first auxiliary heat exchange units 41-1 and 41- are arranged. 2 and the second auxiliary heat exchanging units 42-1 and 42-2 may be arranged in series with respect to the blowing direction of the blowing fan 46.
  • FIG. 6 is a schematic diagram showing the first heat exchange unit 4 in the sixth embodiment.
  • the sixth embodiment is different from the first embodiment in that the heat pump device 500 includes a blower fan 46 and a heating unit 48.
  • the heat pump device 500 includes a blower fan 46 and a heating unit 48.
  • portions common to the first embodiment are denoted by the same reference numerals, description thereof is omitted, and differences from the first embodiment will be mainly described.
  • the first auxiliary heat exchanging part 41 and the second auxiliary heat exchanging part 42 are arranged in series with respect to the blowing direction of the air blown by the blower fan 46.
  • the first auxiliary heat exchanging part 41 is arranged on the upstream side with respect to the blowing direction of the air blown by the blower fan 46.
  • a heating means 48 which is an electric heater is provided between the first sub heat exchange section 41 and the second sub heat exchange section 42, along the second sub heat exchange section 42 on the second sub heat exchange section 42 side.
  • FIG. 7 is a schematic diagram showing the second sub heat exchange unit 42 in the sixth embodiment.
  • the second auxiliary heat exchanging unit 42 has a plurality of plate fins 49 stacked, and two refrigerant tubes 50 penetrate these plate fins 49 in the stacking direction. Yes.
  • the refrigerant pipe 50 is a part of the first circulation path 4a, the second circulation path 4b in the second embodiment, or the refrigerant circuit 8 in other embodiments.
  • the heating means 48 is disposed in parallel with the refrigerant pipe 50 along the outer edge of the second sub heat exchange part 42.
  • the heating means 48 may not be arranged in parallel with the refrigerant pipe 50, and is not attached to the outer edge of the second auxiliary heat exchanging section 42, but is attached to a part of the refrigerant pipe 50 or the plate fin 49. It may be worn or built in.
  • FIG. 8 is a schematic diagram showing a heat pump device 500 according to the sixth embodiment.
  • the refrigerant circuit 8 a of the heat pump device 500 does not include the pressure feed switching unit 3 and the inflow switching unit 5.
  • the expansion device 6 is provided with a plurality of capillary tubes 63 and 64 and shut-off valves 63a and 63b that cause a fixed pressure loss instead of the expansion valve as in the above-described embodiment.
  • the shut-off valves 63a and 63b switch the capillary tubes 63 and 64 through which the refrigerant flows, and flow only through the capillary tube 63, flow through only the capillary tube 64, and neither of the capillary tubes 63 and 64 flows.
  • 64 can be switched to four ways of distribution.
  • the capillary tubes 63 and 64 and the shutoff valves 63a and 64a may not be two sets as shown in FIG. 8, but may be one set or a plurality of sets of three or more. In the case of one set, the adjustment of the circulation amount of the refrigerant becomes coarse, and the adjustment of the circulation amount of the refrigerant becomes finer as the number of combinations increases. Further, when there is one capillary tube 63, the circulation of the refrigerant is not switched, and therefore the shutoff valve may be omitted.
  • the secondary expansion device 43 in the first heat exchange unit 4 is not an expansion valve, but a capillary tube 65 that becomes a fixed pressure loss as in the above embodiment.
  • the compressor 2, the second heat exchanger 7, the plurality of capillary tubes 63 and 64, the expansion device 6 including the shut-off valves 63a and 64a, the first heat exchange unit 4, and the compressor 2 are provided.
  • the refrigerant circulates in this order.
  • the refrigerant from the expansion device 6 flows in the order of the first sub heat exchange unit 41, the sub expansion device 43 including the capillary tube 65, and the second sub heat exchange unit 42. Circulate.
  • the heat pump device 500 according to the sixth embodiment can only dissipate heat from the second heat exchanger 7 to the indoor air 12, and is a heating-only device. For this reason, normal cooling operation, high-temperature defrosting operation, and semi-high temperature defrosting operation cannot be performed, but normal heating operation and defrosting heating operation are possible in the same manner as in the above embodiment, and the same effects as in the above embodiment. Play. Further, since the expansion device 6 and the sub-expansion device 43 are not the expansion valve but are constituted by the capillary tubes 63 and 64 and the capillary tube 65, the reliability is improved because the device is cheaper and smaller, and is less likely to fail.
  • the capillary tubes 63 and 64 and the capillary tube 65 have a narrower range of refrigerant flow or compression ratio than the expansion valve. However, if the heating and defrosting conditions are kept constant, the efficiency of the operating conditions can be improved. Reduction can be suppressed as much as possible.
  • either one or both of the expansion device 6 and the sub expansion device 43 has a variable flow rate or compression ratio range.
  • a wide expansion valve may be used.
  • any one or both of the expansion device 6 and the sub expansion device 43 in the first, second, and third embodiments may be a capillary tube. In this case, an inexpensive, small, and highly reliable heat pump device is realized. be able to.
  • bypass valve 62 and the shutoff valves 63a and 64a may substitute two of these as three-way valves.
  • any piping or valve may be used as long as the distribution path can be switched.
  • FIG. 9 is a schematic diagram showing a heat pump device 600 according to the seventh embodiment.
  • the seventh embodiment is different from the first embodiment in that the heat pump device 600 is applied to the refrigerator 601.
  • portions common to the first embodiment are denoted by the same reference numerals, description thereof will be omitted, and differences from the first embodiment will be mainly described.
  • the heat pump device is applied to an air conditioner that transports heat between the outdoor air 11 and the indoor air 12 by the refrigerant circuit 8 to cool and heat the room.
  • the heat pump device 600 is applied to a refrigerator 601 that stores food or the like at a low temperature.
  • the refrigerator 601 uses the refrigerant circuit 8 to perform defrosting in the cooling unit 104 that is the first heat exchange unit 4.
  • the inside air 51 and the inside air 52 (by the circulation fan 146 (equivalent to the ventilation fan 46 in the said embodiment))
  • the outdoor air 11, 11a, 11b in the above embodiment passes through the circulation path 71 and passes between the interior 70 and the cooling unit 104 (corresponding to the first heat exchange unit 4 in the above embodiment).
  • a first cooler 141 (corresponding to the first sub heat exchange unit 41 in the above embodiment) and a second cooler 142 (second sub heat exchanger in the above embodiment) are provided.
  • the heat exchanging section 42 corresponding to the heat exchanging section 42).
  • the internal air 51 is cooled, that is, the temperature is lowered by heat exchange with the refrigerant flowing in the first cooler 141, and the internal air 52 flows in the second cooler 142. It is cooled, that is, the temperature is lowered by exchanging heat with the refrigerant.
  • a partition plate 147 (corresponding to the partition plate 47 in the fourth embodiment) is provided between the first cooler 141 and the second cooler 142.
  • an air passage change means 72 that is, for example, a baffle plate is provided between the circulation fan 146 and the cooling unit 104 to open or block the air flow.
  • the air passage changing means 72 can take three positions.
  • the air passage change means 72 When the air passage change means 72 is at the position 72a, the air passage to the first cooler 141 is shielded and the circulation of the internal air 51 is interrupted. Moreover, when the ventilation path change means 72 exists in the position 72b, the air path to the 2nd cooler 142 is shielded, and the distribution
  • the refrigerator 601 is provided with a radiator (not shown) for radiating the heat of the interior 70 to the outside, and this radiator is the second heat exchanger in the above embodiment. It corresponds to 7.
  • the radiator in the refrigerator 601 may be replaced with a refrigerant pipe routed along the inside of the external wall surface of the refrigerator 601 instead of a so-called heat exchanger.
  • the in-compartment air 51 and the in-compartment air 52 once cooled by the cooling unit 104 are supplied to the inside 70 and then circulated back to the cooling unit 104 by the circulation path 71.
  • the refrigerant circuit (not shown) through which the refrigerant flows is the same as the air conditioner in the above embodiment.
  • the cooling unit 104 only needs to cool the internal air 51 and the internal air 52. Therefore, at least the normal cooling operation (second heat exchanger in the above embodiment) is used as the refrigerant flow. 7 may absorb the heat and cool the indoor air 12). Thereby, it can suppress that the condensed water by which the indoor air 12 outside the warehouse was cooled adheres to the wall surface etc. outside the warehouse.
  • the air passage change means 72 is arranged at the position 72c in a state where the circulation fan 146 is operated, and the first cooler 141 and the second cooler 141 Both the internal air 51 and the internal air 52 are cooled by the cooler 142.
  • the refrigerant flow in the refrigerant circuit is the first auxiliary heat exchange in the above embodiment. It is the same as the case where only the part 41 is defrosted, and the ventilation path change means 72 is arrange
  • the refrigerant flow in the refrigerant circuit is the second auxiliary heat exchange in the above embodiment. It is the same as the case where only the part 42 is defrosted, and the ventilation path change means 72 is arrange
  • the refrigerator 601 including a plurality of coolers can continue cooling the interior 70 with the other cooler while defrosting one cooler. For this reason, the refrigerator 601 can maintain the temperature of the interior 70 of the refrigerator 601 low even during defrosting, and can maintain the quality of food stored in the interior 70.
  • the refrigerator 601 according to the seventh embodiment has a reduced risk of failure due to fewer necessary switching valves, piping configurations, operation mode switching, and the like as compared to the showcase of Patent Document 2. Reliability is improved. Further, the operation method is simplified, and a small refrigerator 601 can be realized at low cost.
  • the defrost cooling operation since the air blowing is changed by the air passage changing means 72, the heat generated during the defrosting is appropriately prevented from leaking into the interior 70. Thereby, in the refrigerator 601, it can defrost and cool efficiently.
  • one air passage changing means 72 is used to switch whether the internal air 51 and the internal air 52 are circulated to one cooler or both coolers.
  • a plurality of air passage changing means 72 may be used.
  • an air passage changing means 72 that can be opened and closed is provided for each cooler, and the internal air 51 and the internal air 52 are circulated to one cooler or both coolers. Can be switched.
  • the baffle board as the ventilation path change means 72, whether the internal air 51 and the internal air 52 are distribute
  • a blower fan may be provided for each cooler, and the blower path changing means 72 may be realized by switching the operation or stop of the blower fan. In this case, by switching the operation or stop of the blower fan, it is switched whether the internal air 51 and the internal air 52 are circulated to one cooler or both coolers.
  • Embodiment 7 Although the several cooler was arrange

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

Abstract

L'invention concerne un dispositif de pompe à chaleur (1) possédant : un circuit de réfrigérant (8), dans lequel circule un réfrigérant et qui est formé en reliant, au moyen d'une tuyauterie, un compresseur (2), une première unité d'échange thermique (4), un dispositif d'expansion (6) et un second échangeur thermique (7) ; et une unité de commande (21), qui commande le fonctionnement du circuit de réfrigérant (8). Dans ce dispositif de pompe à chaleur (1), la première unité d'échange thermique (4) possède plusieurs sous-unités d'échange thermique reliées en série, et un sous-dispositif d'expansion (43) ménagé entre les multiples sous-unités d'échange thermique. De plus, l'unité de commande (21) possède un moyen de commande de dégivrage (22) qui commande le sous-dispositif d'expansion (43) lorsque les sous-unités d'échange thermique sont dégivrées, de façon à produire une différence entre la pression du réfrigérant circulant sur le côté en amont du sous-dispositif d'expansion (43) et la pression du réfrigérant circulant sur le côté en aval du sous-dispositif d'expansion (43).
PCT/JP2014/067592 2013-12-04 2014-07-01 Dispositif de pompe à chaleur WO2015083392A1 (fr)

Applications Claiming Priority (2)

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JP2013-251439 2013-12-04
JP2013251439A JP2017026159A (ja) 2013-12-04 2013-12-04 ヒートポンプ装置

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109564043A (zh) * 2016-08-01 2019-04-02 尹明镇 热交换器交替型热泵系统
EP3460374A3 (fr) * 2017-09-20 2019-06-05 Hamilton Sundstrand Corporation Combiné échangeur/de dérivation de chaleur rotatif
CN110226068A (zh) * 2017-01-17 2019-09-10 株式会社Ed7 废热回收型混合热泵系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
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CN110062866A (zh) * 2017-04-06 2019-07-26 松下知识产权经营株式会社 空气调节机

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JPS62149761U (fr) * 1986-03-15 1987-09-22
US4722388A (en) * 1986-09-08 1988-02-02 Drury Chauncey R Heat exchanger
WO1997041398A1 (fr) * 1996-05-02 1997-11-06 Store Heat And Produce Energy, Inc. Operation de degivrage pour systemes de pompe a chaleur et de refrigeration
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JP2005069673A (ja) * 2003-08-06 2005-03-17 Gac Corp 冷却ユニットおよび冷却システム
JP2006234375A (ja) * 2005-01-28 2006-09-07 Denso Corp ヒートポンプ式給湯器
DE102005018125A1 (de) * 2005-04-20 2006-10-26 Bernhard Wenzel Kältemittelkreislauf für eine Wärmepumpe
JP2011080741A (ja) * 2009-09-09 2011-04-21 Fujitsu General Ltd ヒートポンプ装置

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Publication number Priority date Publication date Assignee Title
JPS5726376A (en) * 1980-07-24 1982-02-12 Fuji Electric Co Ltd Cooling unit for refrigerating plant
JPS5747176A (en) * 1980-09-02 1982-03-17 Okamura Corp Method of and apparatus for cooling air curtain type refrigerated display case
JPS58178176A (ja) * 1982-04-14 1983-10-19 株式会社岡村製作所 エア−カ−テン式冷蔵ケ−ス等の冷却方法とその装置
JPS62149761U (fr) * 1986-03-15 1987-09-22
US4722388A (en) * 1986-09-08 1988-02-02 Drury Chauncey R Heat exchanger
WO1997041398A1 (fr) * 1996-05-02 1997-11-06 Store Heat And Produce Energy, Inc. Operation de degivrage pour systemes de pompe a chaleur et de refrigeration
JPH10205933A (ja) * 1997-01-20 1998-08-04 Fujitsu General Ltd 空気調和機
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109564043A (zh) * 2016-08-01 2019-04-02 尹明镇 热交换器交替型热泵系统
CN110226068A (zh) * 2017-01-17 2019-09-10 株式会社Ed7 废热回收型混合热泵系统
CN110226068B (zh) * 2017-01-17 2022-05-31 株式会社Ed7 废热回收型混合热泵系统
EP3460374A3 (fr) * 2017-09-20 2019-06-05 Hamilton Sundstrand Corporation Combiné échangeur/de dérivation de chaleur rotatif
US10704847B2 (en) 2017-09-20 2020-07-07 Hamilton Sunstrand Corporation Rotating heat exchanger/bypass combo

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