EP3246637B1 - Refrigeration cycle device - Google Patents

Refrigeration cycle device Download PDF

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Publication number
EP3246637B1
EP3246637B1 EP15877851.4A EP15877851A EP3246637B1 EP 3246637 B1 EP3246637 B1 EP 3246637B1 EP 15877851 A EP15877851 A EP 15877851A EP 3246637 B1 EP3246637 B1 EP 3246637B1
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EP
European Patent Office
Prior art keywords
refrigerant
compressor
suction
flow
bypass
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EP15877851.4A
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German (de)
English (en)
French (fr)
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EP3246637A1 (en
EP3246637A4 (en
Inventor
Tetsuji Saikusa
Kimitaka KADOWAKI
Tomoyoshi Obayashi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3246637A4 publication Critical patent/EP3246637A4/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
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure
    • 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
    • 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
    • F25B2400/0403—Refrigeration circuit bypassing means for 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
    • 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
    • F25B2400/0409—Refrigeration circuit bypassing means for the 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0272—Compressor control by controlling pressure the suction pressure
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the present invention relates to a refrigeration cycle apparatus for a heat pump water heater or other apparatuses.
  • US 2011/132006 A1 describes a refrigeration cycle apparatus using a compressor discharge bypass and a suction bypass combining the flow of the compressor discharge bypass with a refrigerant flow downstream the condenser and routing the combined flow to the suction side of the compressor. Furthermore, a negative pressure prevention valve is controlled such that negative compressor suction pressure is avoided.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2011-252638
  • HFO-1234yf used in the technique disclosed in Patent Literature 1 is refrigerant having a higher boiling point than refrigerant, such as R407C and R410A, having been used. For this reason, the refrigerant has the property that a compressor suction pressure decreases. Thus, when a heating operation is performed under low outdoor air temperature conditions in particular, the operation is performed in a negative pressure state in which a compressor suction pressure is lower than an atmospheric pressure, thereby causing the problem of the occurrence of a disadvantage, such as a malfunction due to suction of air.
  • the present invention has been made to solve a problem like that described above and provides a refrigeration cycle apparatus that, even when refrigerant having a higher boiling point than R407C refrigerant is used, can prevent a compressor suction pressure from falling to or below an atmospheric pressure under low outdoor air temperature conditions and increase reliability.
  • a refrigeration cycle apparatus can be obtained that, even when refrigerant having a higher boiling point than R407C refrigerant is used, can prevent a compressor suction pressure from falling to or below an atmospheric pressure under low outdoor air temperature conditions and increase reliability.
  • Fig. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention and illustrates a state provided while a heating operation (hot-water supply operation) of raising the temperature of water on a load side is being performed.
  • a heating operation hot-water supply operation
  • the refrigeration cycle apparatus includes a main circuit 30 in which a compressor 1, a four-way valve 2, a condenser 3, a main expansion valve 4, and an evaporator 5 are connected in a circle, and through which refrigerant circulates, a bypass 40, and a discharged gas bypass valve 7 serving as a negative pressure regulating valve that regulates a flow rate in the bypass 40.
  • the compressor 1 is constituted by, for example, an inverter compressor capable of controlling capacity, sucks low-temperature low-pressure gas refrigerant, compresses the refrigerant to turn it into a high-temperature high-pressure gas refrigerant state, and discharges thereof.
  • the four-way valve 2 switches a direction in which the high-temperature high-pressure gas refrigerant discharged from the compressor 1 flows to the direction of the condenser 3 or the evaporator 5.
  • the condenser 3 is constituted by a plate-type heat exchanger and exchanges heat between refrigerant flowing through the main circuit 30 and a medium to be subjected to heat exchange supplied from a cooling load (not illustrated) to transfer heat.
  • the main expansion valve 4 reduces the pressure of high-pressure refrigerant to turn the refrigerant into low-pressure two-phase refrigerant.
  • the evaporator 5 is constituted by, for example, a plate-fin-type heat exchanger and exchanges heat between refrigerant and air to evaporate the refrigerant.
  • the bypass 40 includes a discharged gas bypass 6 and a suction bypass 8, and is a circuit that combines a flow of part of refrigerant discharged from the compressor 1 and a flow of refrigerant having flowed out of the condenser 3 into a combined flow to allow the combined flow to flow into a suction side of the compressor 1.
  • the discharged gas bypass 6 bypasses part of discharged refrigerant discharged from the compressor 1 to the suction side of the compressor 1.
  • the discharged gas bypass valve 7 is provided in the discharged gas bypass 6 and regulates a bypass flow rate of discharged gas to be passed through the discharged gas bypass 6.
  • An increase in the opening degree of the discharged gas bypass valve 7 increases a flow rate of refrigerant passing through the discharged gas bypass 6 and returning to the suction side of the compressor 1 and increases a compressor suction pressure.
  • a reduction in the opening degree of the discharged gas bypass valve 7 reduces a flow rate of refrigerant passing through the discharged gas bypass 6 and returning to the suction side of the compressor 1 and reduces a compressor suction pressure.
  • the suction bypass 8 combines a flow of high-pressure refrigerant at an outlet of the condenser 3 into a flow in the discharged gas bypass 6 to allow the flow to flow into the suction side of the compressor 1.
  • a suction bypass valve 9 is provided in the suction bypass 8 and regulates a flow rate of refrigerant to be passed through the suction bypass 8.
  • An increase in the opening degree of the suction bypass valve 9 increases a flow rate of high-pressure refrigerant passing through the suction bypass 8 and flowing into the suction side of the compressor 1 and thus reduces a compressor suction superheat degree.
  • a reduction in the opening degree of the suction bypass valve 9 reduces a flow rate of high-pressure refrigerant flowing from the suction bypass 8 into the suction side of the compressor 1 and thus increases a compressor suction superheat degree.
  • refrigerant containing HFO-1234yf refrigerant or HFO-1234ze refrigerant is used as refrigerant.
  • Refrigerant may be a single refrigerant of HFO-1234yf, a single refrigerant of HFO-1234ze, or a refrigerant mixture containing HFO-1234yf or HFO-1234ze.
  • R32 can be used, for example.
  • a global warming potential (GWP) of the HFO-1234yf refrigerant or the HFO-1234ze refrigerant is "4", which is lower than "2090" of existing R410A refrigerant and "1770" of R407C refrigerant, and thus the HFO-1234yf refrigerant or the HFO-1234ze refrigerant is refrigerant that has less impact on the global environment.
  • the discharged gas bypass valve 7 and the suction bypass valve 9 are fully closed, and refrigerant does not flow through the discharged gas bypass 6 and the suction bypass 8.
  • refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure refrigerant discharged from the compressor 1 flows into the condenser 3 via the four-way valve 2.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant having flowed out of the condenser 3 flows into the main expansion valve 4 and is reduced in pressure and expanded to turn into low-temperature low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant having flowed out of the main expansion valve 4 flows into the evaporator 5, cools air serving as a medium to be subjected to heat exchange, and evaporates to turn into low-temperature low-pressure gas refrigerant.
  • the low-temperature low-pressure gas refrigerant having flowed out of the evaporator 5 passes through the four-way valve 2 again and then is sucked into the compressor 1 again.
  • Fig. 2 is a graph illustrating comparisons of relationships between saturation temperatures and saturated vapor pressures of various types of refrigerant.
  • refrigerant R410A refrigerant, R407C refrigerant, HFO-1234yf refrigerant, and HFO-1234ze are illustrated.
  • the horizontal axis represents saturation temperature [DEGREES C]
  • the vertical axis represents saturated vapor pressure [MPa (abs)].
  • the HFO-1234yf refrigerant used in Embodiment 1 is lower than the R410A refrigerant and R407C refrigerant that have been used.
  • an evaporating temperature may fall below a saturated vapor temperature of -29.5 degrees C at an atmospheric pressure, resulting in a negative pressure operation in which a compressor suction pressure is equal to or less than the atmospheric pressure.
  • the compressor suction pressure becomes negative, air is sucked into the refrigeration cycle, resulting in the occurrence of a disadvantage, such as a malfunction of the refrigeration cycle.
  • the refrigeration cycle apparatus performs a negative pressure prevention operation of continuing a hot-water supply operation with a compressor suction pressure being equal to or greater than a negative pressure even under low outdoor air temperature conditions.
  • Fig. 3 is a P-h diagram illustrating an action state in a negative pressure prevention operation in the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • [1] to [5] respectively indicate refrigerant states at positions of [1] to [5] in Fig. 1 .
  • the opening degree of the main expansion valve 4 is in a substantially-closed state.
  • An opening degree being in the "substantially-closed" state refers to not only an opening degree being in a fully-closed state but also such an exceedingly small opening degree that has no adverse effect in preventing negative pressure.
  • an opening degree being in the "substantially-closed” state corresponds to an opening degree being in a fully-closed state or in a state close to the fully-closed state.
  • refrigerant ([1]) being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure refrigerant ([2]) discharged from the compressor 1 is divided to flow through two flow paths. Refrigerant that is to flow through one flow path flows into the discharged gas bypass 6 and is reduced in pressure by the discharged gas bypass valve 7 to turn into high-temperature low-pressure gas refrigerant ([3]), and it is bypassed to the suction side of the compressor 1.
  • the high-pressure liquid refrigerant having flowed out of the condenser 3 flows into the suction bypass 8 and is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure two-phase gas-liquid refrigerant ([5]).
  • a flow of the high-temperature low-pressure gas ([3]) that has been reduced in pressure by the discharged gas bypass valve 7 and a flow of the low-temperature low-pressure two-phase gas-liquid refrigerant ([5]) that has been reduced in pressure and expanded by the suction bypass valve 9 combine to form a flow of low-temperature low-pressure gas refrigerant ([1]), and the flow is sucked into the compressor 1 again.
  • the main expansion valve 4 is substantially closed during the negative pressure prevention operation, little low-pressure two-phase refrigerant flows into the evaporator 5, and evaporation of refrigerant caused by heat exchange with outdoor air does not occur.
  • the negative pressure prevention operation is started when an operation state in which a compressor suction pressure is close to a negative pressure is entered, and is an operation that causes little refrigerant to flow into the evaporator 5 and causes most of high-pressure refrigerant having flowed out of the condenser 3 to flow into the suction bypass 8. Then, the discharged gas bypass valve 7 is controlled so that a compressor suction pressure becomes higher than the negative pressure, thereby preventing negative pressure. In Embodiment 1, in addition to control of the discharged gas bypass valve 7, the suction bypass valve 9 is also controlled so that a compressor suction superheat degree is put into an appropriate state.
  • Fig. 4 is a system configuration diagram of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • Fig. 5 is a flowchart illustrating a control procedure of a negative pressure prevention operation in the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the refrigeration cycle apparatus includes a controller 20, a compressor suction pressure sensor 21, and a compressor suction temperature sensor 22. Note that the other components are the same as those in Fig. 1 .
  • the controller 20 controls the entire refrigeration cycle apparatus.
  • the controller 20 is constituted by a microcomputer, for example, and includes a CPU, a RAM, a ROM, and other components.
  • a control program and a program corresponding to the flowchart of Fig. 5 are stored.
  • the compressor suction pressure sensor 21 and the compressor suction temperature sensor 22 are connected to the controller 20 so that detection signals from the respective sensors can be received. Based on, for example, these detection signals, the controller 20 controls the opening degree of the main expansion valve 4, the opening degree of the discharged gas bypass valve 7, and the opening degree of the suction bypass valve 9, for example. The controller 20 also controls, based on, for example, detection signals from the respective sensors 21 and 22, various operations including a negative pressure prevention operation.
  • the controller 20 includes a negative pressure prevention control unit 20a and a superheat degree control unit 20b.
  • the negative pressure prevention control unit 20a performs a negative pressure prevention operation of controlling the discharged gas bypass valve 7 to prevent a suction pressure of the compressor 1 from becoming negative.
  • the superheat degree control unit 20b regulates the opening degree of the suction bypass valve 9 so that a degree of superheat of gas to be sucked into the compressor 1 becomes a setting value set in advance.
  • the negative pressure prevention control unit 20a and the superheat degree control unit 20b are functionally configured by the CPU and the control program.
  • the controller 20 acquires a compressor suction pressure Ps detected by the compressor suction pressure sensor 21 (S1). Then, the controller 20 compares the compressor suction pressure Ps with a setting value 1 (It is, for example, 0.01 MPa (G), which is a setting value representing at least a positive pressure.) that has been set in advance and is an upper limit pressure at which a negative pressure prevention operation is started (S2). While the compressor suction pressure Ps is equal to or greater than the setting value 1, the controller 20 returns to step S1, and a normal hot-water supply operation is continued.
  • a setting value 1 It is, for example, 0.01 MPa (G), which is a setting value representing at least a positive pressure.
  • the controller 20 determines that the refrigeration cycle apparatus is in an operation state in which an outdoor air temperature is low and the compressor suction pressure is close to a negative pressure, and starts the negative pressure prevention operation (S3).
  • the controller 20 substantially closes the main expansion valve 4 (its opening degree is reduced to an opening degree being in a fully-closed state or in a state close to the fully-closed state) (S4).
  • the controller 20 compares a setting value 2 (It is, for example, 0.02 MPa (G), which is a setting value representing at least a positive pressure.) that has been set in advance as a target value of a compressor suction pressure with the compressor suction pressure Ps (S5).
  • the controller 20 increases the opening degree of the discharged gas bypass valve 7 (S6).
  • the compressor suction pressure Ps rises and approaches the setting value 2.
  • the opening degree of the discharged gas bypass valve 7 is reduced (S7).
  • the compressor suction pressure Ps falls and approaches the setting value 2. Note that, although not illustrated in Fig. 5 , when the compressor suction pressure Ps is equal to the setting value 2, the opening degree of the discharged gas bypass valve 7 may remain unchanged.
  • the controller 20 acquires a compressor suction temperature Ts detected by the compressor suction temperature sensor 22. Then, the controller 20 calculates a compressor suction superheat degree SHs by using the acquired compressor suction temperature Ts (S9). That is, the controller 20 calculates a saturation temperature f(Ps) of the compressor suction pressure Ps and subtracts the saturation temperature f(Ps) of the compressor suction pressure Ps from the compressor suction temperature Ts to get a compressor suction superheat degree SHs.
  • the controller 20 compares the calculated compressor suction superheat degree SHs with a setting value 3 (for example, 5 K) that has been set in advance as a target value of a compressor suction superheat degree (S10). Then, when the compressor suction superheat degree SHs is lower than the setting value 3, the controller 20 reduces the opening degree of the suction bypass valve 9 (S11). Thus, the compressor suction superheat degree SHs rises and approaches the setting value 3. On the other hand, when the compressor suction superheat degree SHs is higher than the setting value 3, the opening degree of the suction bypass valve 9 is increased (S12). Thus, the compressor suction superheat degree SHs falls and approaches the setting value 3. Note that, although not illustrated in Fig.
  • the opening degree of the suction bypass valve 9 may remain unchanged. Then, after the process of S11 or S12, the controller 20 returns to S5 and repeatedly performs control so that the compressor suction pressure Ps and the compressor suction superheat degree SHs respectively become equal to the corresponding setting value 2 and setting value 3.
  • the refrigeration cycle apparatus when the refrigeration cycle apparatus according to Embodiment 1 enters an operation state in which an outdoor air temperature is low and a compressor suction pressure is close to a negative pressure, the refrigeration cycle apparatus continues a hot-water supply operation with the main expansion valve 4 being fully closed without evaporation of refrigerant in the evaporator 5. Then, the compressor suction pressure is controlled by using the opening degree of the discharged gas bypass valve 7, and a compressor suction superheat degree is also controlled by using the opening degree of the suction bypass valve 9. This prevents the compressor suction pressure from becoming negative and also enables the hot-water supply operation to continue with the compressor suction superheat degree being appropriate.
  • Embodiment 2 a two-way valve is further included in the structure in Embodiment 1 illustrated in Fig. 1 . Note that the other components are the same as those in Fig. 1 . A description will be given below with emphasis on a respect in which Embodiment 2 differs from Embodiment 1.
  • Fig. 6 is a system configuration diagram of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • Fig. 7 is a flowchart illustrating a control procedure of a negative pressure prevention operation in the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • the refrigeration cycle apparatus according to Embodiment 2 further includes a two-way valve 10 in addition to the structure in Embodiment 1.
  • the two-way valve 10 is disposed between the four-way valve 2 and the evaporator 5 and interrupts the flow of refrigerant between the four-way valve 2 and the evaporator 5 by closing the two-way valve 10.
  • a negative pressure prevention operation in the refrigeration cycle apparatus according to Embodiment 2 differs from that in Embodiment 1 in that a step of closing the two-way valve 10 (S21) is further included in the flowchart in Embodiment 1 illustrated in Fig. 5 , and the other steps are the same as those in Embodiment 1. It is only necessary that the step of closing the two-way valve 10 be provided between step S3 and step S5.
  • the refrigeration cycle apparatus produces the same effect as that in Embodiment 1 and also produces the following effect. That is, closing the two-way valve 10 during a negative pressure prevention operation can prevent low-pressure high-temperature refrigerant (refrigerant indicated by a dotted arrow in Fig. 6 ) having flowed out of the discharged gas bypass valve 7 from flowing into the cold evaporator 5 via the four-way valve 2, condensing, and accumulating. This does not result in any lack of refrigerant circulating through the discharged gas bypass 6 and the suction bypass 8 and enables the negative pressure prevention operation to continue.
  • low-pressure high-temperature refrigerant refrigerant indicated by a dotted arrow in Fig. 6
  • Embodiment 3 an ejector and a suction pipe are further included in the structure in Embodiment 1 illustrated in Fig. 1 . Note that the other components are the same as those in Fig. 1 . A description will be given below with emphasis on a respect in which Embodiment 3 differs from Embodiment 1.
  • Fig. 8 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 3 of the present invention.
  • An ejector 11 is disposed on a downstream side of the discharged gas bypass valve 7 of the discharged gas bypass 6 and sucks refrigerant on an evaporator 5 side via a suction pipe 12.
  • Fig. 9 is a schematic view of the ejector of Fig. 8 .
  • the ejector 11 is constituted by three sections: a nozzle 11a, an expansion section 11b, and a diffuser 11c.
  • a main flow flowing in from an inlet is throttled by the nozzle 11a and put into a state in which its flow velocity at the expansion section 11b is higher than that at the inlet.
  • the pressure, flow velocity, and density of refrigerant at the inlet are respectively P1, v1, and p1
  • the pressure, flow velocity, and density of refrigerant at the expansion section 11b are respectively P2, v2, and p2
  • P 1 + 1 2 ⁇ 1 ⁇ 1 2 P 2 + 1 2 ⁇ 2 ⁇ 2 2 2
  • refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure refrigerant discharged from the compressor 1 is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the discharged gas bypass 6 and is reduced in pressure by the discharged gas bypass valve 7 to turn into high-temperature low-pressure gas refrigerant, and it flows into the ejector 11.
  • a refrigerant pressure decreases as a refrigerant flow velocity increases, and refrigerant on the evaporator 5 side is sucked via the suction pipe 12 connected to the refrigerant suction section 11d.
  • Divided high-temperature high-pressure gas refrigerant that is to flow through the other flow path flows into the condenser 3 via the four-way valve 2.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant having flowed out of the condenser 3 flows into the suction bypass 8 and is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure two-phase gas-liquid refrigerant.
  • a flow of the high-temperature low-pressure gas that has been reduced in pressure by the discharged gas bypass valve 7 and passed through the ejector 11 and a flow of the low-temperature low-pressure two-phase gas-liquid refrigerant that has been reduced in pressure and expanded by the suction bypass valve 9 combine to form a flow of low-temperature low-pressure gas refrigerant, and the flow is sucked into the compressor 1 again.
  • the refrigeration cycle apparatus produces the same effect as that in Embodiment 1 and also produces the following effect. That is, even when low-pressure high-temperature refrigerant having flowed out of the discharged gas bypass valve 7 flows into the cold evaporator 5 via the four-way valve 2 during a negative pressure prevention operation, the refrigerant having flowed to the evaporator 5 side is sucked by the ejector 11 to enable the refrigerant to be drawn back to the discharged gas bypass 6.
  • refrigerant having flowed out of the discharged gas bypass valve 7 and flowed into the evaporator 5 can be prevented from condensing and accumulating in the evaporator 5. This does not result in any lack of refrigerant circulating through the discharged gas bypass 6 and the suction bypass 8 and enables the negative pressure prevention operation to continue.
  • Embodiment 4 a receiver is further included in the structure in Embodiment 1 illustrated in Fig. 1 . Note that the other components are the same as those in Fig. 1 . A description will be given below with emphasis on a respect in which Embodiment 4 differs from Embodiment 1.
  • Fig. 10 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 4 of the present invention.
  • a receiver 13 is disposed on a pipe connecting the condenser 3 and the suction bypass valve 9 and stores excess refrigerant caused during an operation.
  • refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure refrigerant discharged from the compressor 1 is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the discharged gas bypass 6 and is reduced in pressure by the discharged gas bypass valve 7 to turn into high-temperature low-pressure gas refrigerant, and it is bypassed to the suction side of the compressor 1.
  • Divided high-temperature high-pressure gas refrigerant that is to flow through the other flow path flows into the condenser 3 via the four-way valve 2.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant having flowed out of the condenser 3 flows into the suction bypass 8 via the receiver 13 and is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure two-phase gas-liquid refrigerant.
  • a flow of the high-temperature low-pressure gas that has been reduced in pressure by the discharged gas bypass valve 7 and a flow of the low-temperature low-pressure two-phase gas-liquid refrigerant that has been reduced in pressure and expanded by the suction bypass valve 9 combine to form a flow of low-temperature low-pressure gas refrigerant, and the flow is sucked into the compressor 1 again.
  • the refrigeration cycle apparatus produces the same effect as that in Embodiment 1 and also produces the following effect. That is, excess refrigerant can be stored in the receiver 13 during a negative pressure prevention operation, thereby preventing an operation in which liquid flows back to the suction side of the compressor 1 and enabling a highly reliable negative pressure prevention operation to continue.
  • Embodiment 4 presents the structure including a refrigerant storage container (the receiver 13 herein), the disposition of the refrigerant storage container is not limited to the disposition illustrated in Fig. 10 , and modifications can be made as described in the following Modifications 1 and 2.
  • Fig. 11 is a refrigerant circuit diagram of a refrigeration cycle apparatus illustrating Modification 1 of the refrigeration cycle apparatus according to Embodiment 4 of the present invention.
  • a refrigerant circuit of Modification 1 of the refrigeration cycle apparatus according to Embodiment 4 includes a receiver 13a and a check valve 14 in place of the receiver 13 of Fig. 10 . Note that the other components are the same as those in Fig. 10 .
  • the receiver 13a is a refrigerant storage container that stores excess refrigerant caused during an operation.
  • the receiver 13a is provided in parallel with the main circuit 30 on an outlet side of the condenser 3. In other words, the receiver 13a is provided in parallel with a pipe between a portion where an upstream end of the suction bypass 8 meets the main circuit 30 and the outlet of the condenser 3.
  • the check valve 14 prevents refrigerant from flowing from a main expansion valve 4 side into the receiver 13a.
  • frost forms on the evaporator 5 during a hot-water supply operation.
  • a reverse defrosting operation is performed.
  • the reverse defrosting operation is an operation of removing frost forming on the evaporator 5 by switching the four-way valve 2 in directions indicated by dotted lines in Fig. 11 to supply high-temperature high-pressure gas refrigerant discharged from the compressor 1 to the evaporator 5.
  • the check valve 14 prevents refrigerant from flowing into the receiver 13a during the reverse defrosting operation.
  • refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure refrigerant discharged from the compressor 1 is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the discharged gas bypass 6 and is reduced in pressure by the discharged gas bypass valve 7 to turn into high-temperature low-pressure gas refrigerant, and it is bypassed to the suction side of the compressor 1.
  • Divided high-temperature high-pressure gas refrigerant that is to flow through the other flow path flows into the condenser 3 via the four-way valve 2.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant.
  • the high-pressure refrigerant having flowed out of the condenser 3 is divided to flow through two flow paths. Refrigerant that is to flow through one flow path flows into the suction bypass 8 via the main circuit 30, and refrigerant that is to flow through the other flow path is condensed and stored in the receiver 13a.
  • the high-pressure refrigerant having flowed into the suction bypass 8 is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure two-phase gas-liquid refrigerant.
  • a flow of the high-temperature low-pressure gas that has been reduced in pressure by the discharged gas bypass valve 7 and a flow of the low-temperature low-pressure two-phase gas-liquid refrigerant that has been reduced in pressure and expanded by the suction bypass valve 9 combine to form a flow of low-temperature low-pressure gas refrigerant, and the flow is sucked into the compressor 1 again.
  • the receiver 13a is provided in parallel with the main circuit 30 on the outlet side of the condenser 3. This enables excess refrigerant to be stored in the receiver 13a even when refrigerant at the outlet of the condenser 3 is in a two-phase state.
  • an operation in which liquid flows back to the suction side of the compressor 1 is prevented, thereby enabling a highly reliable negative pressure prevention operation to continue.
  • Fig. 12 is a refrigerant circuit diagram of a refrigeration cycle apparatus illustrating Modification 2 of the refrigeration cycle apparatus according to Embodiment 4 of the present invention.
  • a refrigerant circuit of Modification 2 of the refrigeration cycle apparatus according to Embodiment 4 includes an accumulator 15 in place of the receiver 13 of Fig. 10 . Note that the other components are the same as those in Fig. 10 .
  • the accumulator 15 is provided on the suction side of the compressor 1 and is a refrigerant storage container that stores excess refrigerant caused during an operation.
  • refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure refrigerant discharged from the compressor 1 is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the discharged gas bypass 6 and is reduced in pressure by the discharged gas bypass valve 7 to turn into high-temperature low-pressure gas refrigerant, and it is bypassed to the suction side of the compressor 1.
  • Divided high-temperature high-pressure gas refrigerant that is to flow through the other flow path flows into the condenser 3 via the four-way valve 2.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant.
  • the high-pressure refrigerant having flowed out of the condenser 3 flows into the suction bypass 8, and the high-pressure refrigerant having flowed into the suction bypass 8 is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure two-phase gas-liquid refrigerant.
  • a flow of the high-temperature low-pressure gas that has been reduced in pressure by the discharged gas bypass valve 7 and a flow of the low-temperature low-pressure two-phase gas-liquid refrigerant that has been reduced in pressure and expanded by the suction bypass valve 9 combine to form a flow of low-temperature low-pressure refrigerant, and the flow is sucked into the compressor 1 again via the accumulator 15.
  • the accumulator 15 is provided on the suction side of the compressor 1, thereby enabling excess refrigerant to be stored in the accumulator 15 during a negative pressure prevention operation in which excess refrigerant is caused. This prevents an operation in which liquid flows back to the suction side of the compressor 1, thereby enabling a highly reliable negative pressure prevention operation to continue.
  • Embodiments 1 to 4 described above part of refrigerant discharged from the compressor 1 toward the condenser 3 is caused to flow into the discharged gas bypass 6 so that it is diverted from the main circuit 30, and the diverted refrigerant is caused to flow back to the suction side of the compressor 1. Then, in causing the diverted refrigerant to flow back to the suction side of the compressor 1, a flow of the diverted refrigerant is combined with a flow of refrigerant flowing through the suction bypass 8 on a downstream side of the suction bypass valve 9 and then caused to flow back.
  • Embodiment 5 in causing diverted refrigerant that has been diverted from the main circuit 30 to flow back to the suction side of the compressor 1, a flow of the diverted refrigerant is combined with a flow of refrigerant that is to flow through the suction bypass 8 on an upstream side of the suction bypass valve 9 and then caused to flow back.
  • Fig. 13 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 5 of the present invention and illustrates a state provided while a hot-water supply operation of raising the temperature of water on a load side is being performed. Furthermore, Fig. 14 is a P-h diagram illustrating an action state in an operation in Fig. 13 .
  • Embodiment 5 the discharged gas bypass 6 and the discharged gas bypass valve 7 are removed from the structure in Embodiment 1 illustrated in Fig. 1 , whereas a condenser bypass 16 that bypasses the condenser 3 and a condenser bypass valve 17 that regulates a flow rate in the condenser bypass 16 are included.
  • a bypass 41 in Embodiment 5 includes the condenser bypass 16 and the suction bypass 8, and is a circuit that combines a flow of refrigerant having flowed out of the condenser bypass 16 (part of refrigerant discharged from the compressor 1) and a flow of refrigerant having flowed out of the condenser 3 into a combined flow to allow the combined flow to flow into the suction side of the compressor 1 via the suction bypass 8.
  • the suction bypass valve 9 constitutes the negative pressure regulating valve according to the present invention.
  • the condenser bypass 16 bypasses part of discharged refrigerant discharged from the compressor 1 to the outlet side of the condenser 3.
  • the condenser bypass valve 17 regulates a bypass flow rate of discharged gas to be passed through the condenser bypass 16.
  • refrigerant ([1]) being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas ([2]), and discharged.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 2 and then is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the condenser bypass 16 and is reduced in pressure ([3]) by the condenser bypass valve 17, and then it flows out of the condenser bypass 16.
  • a flow of the high-temperature high-pressure gas refrigerant having flowed out of the condenser bypass 16 and a flow of the high-pressure liquid refrigerant having flowed out of the condenser 3 combine to form a flow of high-pressure high-quality two-phase refrigerant ([5]).
  • the two-phase refrigerant flows into the suction bypass 8 and is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure gas refrigerant ([1]), and the low-temperature low-pressure gas refrigerant is sucked into the compressor 1 again.
  • the main expansion valve 4 is substantially closed during the negative pressure prevention operation, little low-pressure two-phase refrigerant flows into the evaporator 5, and evaporation of refrigerant caused by heat exchange with outdoor air does not occur.
  • a compressor suction pressure is controlled by the discharged gas bypass valve 7.
  • a flow of refrigerant ([3]) having flowed out of the condenser bypass 16 and a flow of refrigerant ([4]) having flowed out of the condenser 3 combine to form a combined flow, and refrigerant in the combined flow is reduced in pressure by the suction bypass valve 9 and sucked into the compressor 1.
  • a compressor suction pressure is controlled by the suction bypass valve 9.
  • Fig. 15 is a system configuration diagram of the refrigeration cycle apparatus according to Embodiment 5 of the present invention.
  • the refrigeration cycle apparatus differs from that illustrated in Fig. 4 in that the controller 20 is connected in such a manner as to be able to control the condenser bypass valve 17 in place of the discharged gas bypass valve 7 in the system configuration in Embodiment 1 illustrated in Fig. 4 .
  • the controller 20 includes a negative pressure prevention control unit 20A and a superheat degree control unit 20B.
  • the negative pressure prevention control unit 20A performs a negative pressure prevention operation of controlling the opening degree of the suction bypass valve 9 to prevent a suction pressure of the compressor 1 from becoming negative.
  • the superheat degree control unit 20B regulates the opening degree of the condenser bypass valve 17 so that a degree of superheat of gas to be sucked into the compressor 1 becomes a setting value set in advance.
  • the negative pressure prevention control unit 20A and the superheat degree control unit 20B are functionally configured by the CPU and the control program. Configurations other than these are the same as those illustrated in Fig. 4 .
  • Fig. 16 is a flowchart illustrating a control procedure of a negative pressure prevention operation in the refrigeration cycle apparatus according to Embodiment 5 of the present invention.
  • the flowchart in Embodiment 5 illustrated in Fig. 16 differs from that in Embodiment 1 in the following respects. That is, control of the opening degree of the discharged gas bypass valve 7 in steps S6 and S7 in Fig. 5 is replaced with control of the opening degree of the suction bypass valve 9 in steps S6a and S7a in Fig. 16 . Furthermore, control of the opening degree of the suction bypass valve 9 in steps S11 and S12 in Fig.
  • Embodiment 5 is replaced with control of the opening degree of the condenser bypass valve 17 in Fig. 16 .
  • the other steps are the same as those in the control flowchart of Fig. 5 .
  • a description will be given below with emphasis on a respect in which control of the negative pressure prevention operation in Embodiment 5 differs from that in Embodiment 1.
  • Embodiment 5 as a result of a comparison of a compressor suction pressure Ps and a setting value 2 set in advance in step S5, when the compressor suction pressure Ps is lower than the setting value 2, the opening degree of the suction bypass valve 9 is increased (S6a). Thus, the compressor suction pressure Ps rises and approaches the setting value 2. On the other hand, when the compressor suction pressure Ps is higher than the setting value 2, the opening degree of the suction bypass valve 9 is reduced (S7a). Thus, the compressor suction pressure Ps falls and approaches the setting value 2.
  • Embodiment 5 as a result of a comparison of a compressor suction superheat degree SHs and a setting value 3 that has been set in advance as a target value of a compressor suction superheat degree in step S10, when the compressor suction superheat degree SHs is lower than the setting value 3, the controller 20 increases the opening degree of the condenser bypass valve 17 (S11a). Thus, the compressor suction superheat degree SHs rises and approaches the setting value 3. On the other hand, when the compressor suction superheat degree SHs is higher than the setting value 3, the opening degree of the condenser bypass valve 17 is reduced (S12a). Thus, the compressor suction superheat degree SHs falls and approaches the setting value 3. Then, after the process of S11a or S12a, the controller 20 returns to S5 and repeatedly performs control so that the compressor suction pressure Ps and the compressor suction superheat degree SHs respectively become equal to the corresponding setting value 2 and setting value 3.
  • the refrigeration cycle apparatus differs from that in Embodiment 1 in bypass valves to be controlled, but can produce the same effect as that in Embodiment 1. That is, when an operation state in which an outdoor air temperature is low and a compressor suction pressure is close to a negative pressure is entered, a hot-water supply operation is continued with the main expansion valve 4 being fully closed without evaporation of refrigerant in the evaporator 5. Then, the compressor suction pressure is controlled by using the opening degree of the suction bypass valve 9, and a suction superheat degree of the compressor 1 is also controlled by using the opening degree of the condenser bypass valve 17.
  • Embodiment 6 corresponds to, so to speak, a combination of Embodiment 5 and Embodiment 4 in which the receiver 13 is included. A description will be given below with emphasis on a respect in which Embodiment 6 differs from Embodiment 5.
  • Fig. 17 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 6 of the present invention.
  • a system configuration diagram of the refrigeration cycle apparatus according to Embodiment 6 includes the receiver 13. Note that the other components are the same as those in Embodiment 5 illustrated in Fig. 13 .
  • the receiver 13 is disposed on a pipe connecting the condenser 3 and the suction bypass valve 9 and stores excess refrigerant caused during an operation.
  • Refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 2 and then is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the condenser bypass 16 and is reduced in pressure by the condenser bypass valve 17, and then it flows out of the condenser bypass 16.
  • Divided high-temperature high-pressure gas refrigerant that is to flow through the other flow path flows into the condenser 3.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant and flows into the receiver 13.
  • a flow of the high-temperature high-pressure gas refrigerant having flowed out of the condenser bypass 16 and a flow of the high-pressure liquid refrigerant having flowed out of the receiver 13 combine to form a flow of high-pressure high-quality two-phase refrigerant, and the flow flows into the suction bypass 8.
  • the two-phase refrigerant having flowed into the suction bypass 8 is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure gas refrigerant, and the low-temperature low-pressure gas refrigerant is sucked into the compressor 1 again.
  • the refrigeration cycle apparatus produces the same effect as that in Embodiment 5 and also produces the following effect. That is, excess refrigerant can be stored in the receiver 13 during a negative pressure prevention operation, thereby preventing an operation in which liquid flows back to the suction side of the compressor 1 and enabling a highly reliable negative pressure prevention operation to continue.
  • Embodiment 6 presents the structure including a refrigerant storage container (the receiver 13 herein), the disposition of the refrigerant storage container is not limited to the disposition illustrated in Fig. 17 , and modifications can be made as described in the following Modifications 1 and 2.
  • Fig. 18 is a refrigerant circuit diagram of Modification 1 of the refrigeration cycle apparatus according to Embodiment 6 of the present invention.
  • a refrigerant circuit of Modification 1 of the refrigeration cycle apparatus according to Embodiment 6 includes the receiver 13a and the check valve 14 in place of the receiver 13 of Fig. 17 .
  • the other components are the same as those in Fig. 17 .
  • the receiver 13a is a refrigerant storage container that stores excess refrigerant caused during an operation.
  • the receiver 13a is provided in parallel with the main circuit 30 on the outlet side of the condenser 3. In other words, the receiver 13a is provided in parallel with a pipe between a portion where a downstream end of the condenser bypass 16 meets the main circuit 30 and the outlet of the condenser 3.
  • the check valve 14 prevents refrigerant from flowing from the main expansion valve 4 side into the receiver 13a.
  • frost forms on the evaporator 5 during a hot-water supply operation.
  • a reverse defrosting operation is performed.
  • the reverse defrosting operation is an operation of removing frost forming on the evaporator 5 by switching the four-way valve 2 in directions indicated by dotted lines in Fig. 18 to supply high-temperature high-pressure gas refrigerant discharged from the compressor 1 to the evaporator 5.
  • the check valve 14 prevents the inflow of refrigerant during the reverse defrosting operation.
  • refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 2 and then is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the condenser bypass 16 and is reduced in pressure by the condenser bypass valve 17, and then it flows out of the condenser bypass 16.
  • Divided high-temperature high-pressure gas refrigerant that is to flow through the other flow path flows into the condenser 3.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant.
  • the high-pressure refrigerant having flowed out of the condenser 3 is divided to flow through two flow paths. Refrigerant that is to flow through one flow path flows into the main circuit 30, and refrigerant that is to flow through the other flow path is condensed and stored in the receiver 13a. A flow of the high-pressure refrigerant having flowed into the main circuit 30 combines with a flow of the high-temperature high-pressure gas refrigerant having flowed out of the condenser bypass 16 to form a flow of high-pressure high-quality two-phase refrigerant.
  • the two-phase refrigerant flows into the suction bypass 8 and is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure gas refrigerant, and the low-temperature low-pressure gas refrigerant is sucked into the compressor 1 again.
  • the receiver 13a is provided in parallel with the main circuit 30 on the outlet side of the condenser 3. This enables excess refrigerant to be stored in the receiver 13a even when refrigerant at the outlet of the condenser 3 is in a two-phase state.
  • an operation in which liquid flows back to the suction side of the compressor 1 is prevented, thereby enabling a highly reliable negative pressure prevention operation to continue.
  • Fig. 19 is a refrigerant circuit diagram of Modification 2 of the refrigeration cycle apparatus according to Embodiment 6 of the present invention.
  • a refrigerant circuit of Modification 2 of the refrigeration cycle apparatus according to Embodiment 6 includes the accumulator 15 in place of the receiver 13 of Fig. 17 . Note that the other components are the same as those in Fig. 17 .
  • the accumulator 15 is provided on the suction side of the compressor 1 and stores excess refrigerant caused during an operation.
  • refrigerant being in a low-temperature low-pressure gas state is sucked into the compressor 1, compressed to turn into high-temperature high-pressure gas, and discharged.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 2 and then is divided to flow through two flow paths.
  • Refrigerant that is to flow through one flow path flows into the condenser bypass 16 and is reduced in pressure by the condenser bypass valve 17, and then it flows out of the condenser bypass 16.
  • Divided high-temperature high-pressure gas refrigerant that is to flow through the other flow path flows into the condenser 3.
  • the high-temperature high-pressure gas refrigerant having flowed into the condenser 3 transfers heat to water serving as a medium to be subjected to heat exchange to turn into high-pressure liquid refrigerant.
  • a flow of the high-temperature high-pressure gas refrigerant having flowed out of the condenser bypass 16 and a flow of the high-pressure liquid refrigerant having flowed out of the condenser 3 combine to form a flow of high-pressure high-quality two-phase refrigerant, and the flow flows into the suction bypass 8.
  • the two-phase refrigerant having flowed into the suction bypass 8 is reduced in pressure and expanded by the suction bypass valve 9 to turn into low-temperature low-pressure refrigerant, and the low-temperature low-pressure refrigerant is sucked into the compressor 1 again via the accumulator 15.
  • the accumulator 15 is provided on the suction side of the compressor 1, thereby enabling excess refrigerant to be stored in the accumulator 15 during a negative pressure prevention operation in which excess refrigerant is caused. This prevents an operation in which liquid flows back to the suction side of the compressor 1, thereby enabling a highly reliable negative pressure prevention operation to continue.
  • refrigerant a single refrigerant of HFO-1234yf, a single refrigerant of HFO-1234ze, or a refrigerant mixture of HFO-1234yf or HFO-1234ze and R32 is used.
  • refrigerant may be any refrigerant that has a higher boiling point than R407C.
  • refrigerant it is desirable that refrigerant be refrigerant whose global warming potential is lower than that of R407C.
  • the refrigeration cycle apparatus is used for a heat pump water heater
  • the refrigeration cycle apparatus can also be used for an air-conditioning apparatus, for example.

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  • Mechanical Engineering (AREA)
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  • Heat-Pump Type And Storage Water Heaters (AREA)
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WO2016113899A1 (ja) 2016-07-21
EP3246637A1 (en) 2017-11-22
EP3246637A4 (en) 2018-12-26
JP6275283B2 (ja) 2018-02-07
JPWO2016113899A1 (ja) 2017-07-13

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