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EP3594592B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3594592B1
EP3594592B1 EP17899458.8A EP17899458A EP3594592B1 EP 3594592 B1 EP3594592 B1 EP 3594592B1 EP 17899458 A EP17899458 A EP 17899458A EP 3594592 B1 EP3594592 B1 EP 3594592B1
Authority
EP
European Patent Office
Prior art keywords
mode
flow path
refrigerant
heat exchanger
refrigeration cycle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17899458.8A
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English (en)
French (fr)
Other versions
EP3594592A1 (de
EP3594592A4 (de
Inventor
Satoru Yanachi
Hirokazu Minamisako
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3594592A1 publication Critical patent/EP3594592A1/de
Publication of EP3594592A4 publication Critical patent/EP3594592A4/de
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Publication of EP3594592B1 publication Critical patent/EP3594592B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0291—Control issues related to the pressure of the indoor unit
    • 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
    • F25B2313/029—Control issues
    • F25B2313/0292—Control issues related to reversing 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
    • 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
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus in which the circulation direction of refrigerant is switched such that a heat exchanger that has been functioning as an evaporator in a heating mode is caused to function as a condenser, thereby defrosting the heat exchanger.
  • Japanese Patent Laying-Open No. 2011-174662 discloses an air heat source heat pump water heater/air-conditioner, in which a pump down operation for collecting refrigerant in a receiver is performed before a refrigerant circuit is switched by a four-way valve from a heating cycle to a cooling cycle, to thereby start a defrosting operation.
  • the first heat exchanger connected to a discharge port of a compressor and functioning as a condenser in a heating mode is connected to a suction port of the compressor.
  • the second heat exchanger connected to the suction port of the compressor and functioning as an evaporator in the heating mode is connected to the discharge port of the compressor in the defrosting mode.
  • the first heat exchanger connected to the discharge port (high pressure side) of the compressor is higher in pressure than the second heat exchanger connected to the suction port (low pressure side) of the compressor.
  • a differential pressure in the heating mode remains between the first heat exchanger and the second heat exchanger.
  • the defrosting mode is started to cause the compressor to operate in the state where the differential pressure remains, a large amount of refrigerant may be moved from the first heat exchanger to the second heat exchanger.
  • the pressure and the temperature in the first heat exchanger decreases.
  • Such a temperature decrease in the first heat exchanger may lead to, for example, dew condensation in the refrigeration cycle apparatus, or damage to a pipe by solidification of a heat medium such as water conveying heat to a heating terminal as a result of heat exchange with refrigerant in the first heat exchanger. Consequently, it may become difficult to stabilize the operation of the refrigeration cycle apparatus.
  • An object of the present invention is to suppress a temperature decrease at the start of a defrosting mode in a heat exchanger that has been functioning as a condenser in a heating mode.
  • a refrigeration cycle apparatus according to the present invention is as set forth in claim 1.
  • the operation mode when the operation mode is switched from the heating mode to the defrosting mode, the operation mode is switched in order of the heating mode, the pressure equalization mode, and the defrosting mode.
  • the pressure equalization mode the flow regulating valve is opened, so that refrigerant on the high pressure side flows through the flow regulating valve to the low voltage side.
  • the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low voltage side is smaller at the end of the pressure equalization mode (at the start of the defrosting mode) than at the start of the pressure equalization mode (at the end of the heating mode).
  • the flow path resistance in proportion to the degree of opening of the flow regulating valve is greater than the flow path resistance of the flow path switching device.
  • the amount of refrigerant flowing out of the first heat exchanger in the pressure equalization mode can be reduced.
  • the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side can be set to be smaller at the start of the defrosting mode than at the end of the heating mode.
  • the pressure equalization mode is adopted before the defrosting mode, so that the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is set to be smaller at the start of the defrosting mode than at the end of the heating mode.
  • the amount of refrigerant flowing out of the first heat exchanger at the start of the defrosting mode can be reduced. Accordingly, a temperature decrease in the first heat exchanger at the start of the defrosting mode can be suppressed. As a result, the refrigeration cycle apparatus can be stably operated.
  • Fig. 1 is a diagram showing the function configuration of a refrigeration cycle apparatus 1 according to the first reference arrangement, together with the flow of refrigerant in a heating mode.
  • the first arrangement is not an embodiment of the invention, but is included to provide additional explanation of the invention.
  • the operation mode of refrigeration cycle apparatus 1 includes a heating mode and a defrosting mode.
  • refrigeration cycle apparatus 1 includes a compressor 11, a heat exchanger 12, an expansion valve 13, a heat exchanger 14, a four-way valve 15, an on-off valve 16, and a controller 17.
  • the refrigerant circulates sequentially through compressor 11, four-way valve 15, heat exchanger 12, expansion valve 13, and heat exchanger 14.
  • On-off valve 16 corresponds to a flow regulating valve of the present invention.
  • Compressor 11 adiabatically compresses refrigerant of gas (gas refrigerant) of low pressure and discharges gas refrigerant of high pressure.
  • four-way valve 15 serves to connect the discharge port of compressor 11 and heat exchanger 12, and also connect heat exchanger 14 and the suction port of compressor 11.
  • four-way valve 15 forms a flow path such that the refrigerant circulates sequentially through compressor 11, four-way valve 15, heat exchanger 12, expansion valve 13, and heat exchanger 14.
  • Heat exchanger 12 functions as a condenser in the heating mode.
  • the gas refrigerant from compressor 11 emits condensation heat and condenses in heat exchanger 12, and then, turns into refrigerant of liquid (liquid refrigerant).
  • heat exchanger 12 heat exchange is performed between the refrigerant and a heat medium that conveys heat to a heating terminal 100.
  • the heat medium may be water or brine (salt water).
  • expansion valve 13 By expansion valve 13, the liquid refrigerant is adiabatically expanded and decompressed, and then, caused to flow out as moist vapor in a gas-liquid two-phase state.
  • an electronic controlled-type expansion valve linear expansion valve: LEV
  • LEV linear expansion valve
  • Heat exchanger 14 is disposed outdoors and functions as an evaporator in a heating mode.
  • the moist vapor from expansion valve 13 is evaporated as a result of absorption of vaporization heat from the outside air in heat exchanger 14.
  • On-off valve 16 is connected in parallel with compressor 11 between the discharge port and the suction port of compressor 11.
  • the flow path resistance of on-off valve 16 is greater than the flow path resistance of four-way valve 15.
  • the flow path resistance of the on-off valve represents a flow path resistance at the time when the on-off valve is opened (the degree of opening shows the fully-opened state). In other words, when on-off valve 16 is opened, the Cv value of on-off valve 16 is smaller than the Cv value of four-way valve 15. In the heating mode, on-off valve 16 is closed.
  • Controller 17 switches the operation mode of refrigeration cycle apparatus 1. Controller 17 controls the driving frequency of compressor 11 to control the amount of refrigerant discharged from compressor 11 per unit time. Controller 17 controls four-way valve 15 to switch the circulation direction of the refrigerant. Controller 17 controls the degree of opening of expansion valve 13. Controller 17 controls on-off valve 16 to be opened and closed. Controller 17 obtains the pressure of the refrigerant at the suction port (suction pressure) of compressor 11 and the pressure of the refrigerant at the discharge port (discharge pressure) of compressor 11 from pressure sensors S1 and S2, respectively. Then, controller 17 calculates the differential pressure between the discharge pressure and the suction pressure.
  • frost may be formed on heat exchanger 14 disposed outdoors and functioning as an evaporator.
  • frost When frost is formed on heat exchanger 14, the heat exchange efficiency of heat exchanger 14 functioning as an evaporator deteriorates, so that the performance of refrigeration cycle apparatus 1 deteriorates.
  • refrigeration cycle apparatus 1 when frost is formed on heat exchanger 14, the heating mode is interrupted, and the defrosting mode for removing the frost formed on heat exchanger 14 is started.
  • Fig. 2 is a diagram showing the function configuration of refrigeration cycle apparatus 1 in Fig. 1 , together with the flow of refrigerant in the defrosting mode.
  • four-way valve 15 serves to connect the discharge port of compressor 11 and heat exchanger 14, and also connect heat exchanger 12 and the suction port of compressor 11.
  • four-way valve 15 forms a flow path such that refrigerant circulates sequentially through compressor 11, four-way valve 15, heat exchanger 14, expansion valve 13, and heat exchanger 12.
  • heat exchanger 14 functions as a condenser. In heat exchanger 14, the condensation heat emitted during liquefaction of the refrigerant dissolves the frost formed on heat exchanger 14, thereby removing the frost.
  • heat exchanger 12 connected to the high pressure side in the heating mode is connected to the low pressure side.
  • heat exchanger 14 connected to the low pressure side in the heating mode is connected to the high pressure side.
  • the pressure in heat exchanger 12 connected to the high pressure side is higher than the pressure in heat exchanger 14 connected to the low pressure side.
  • the differential pressure in the heating mode remains between heat exchanger 12 and heat exchanger 14.
  • the operation mode is switched in order of the heating mode, the pressure equalization mode, and the defrosting mode.
  • the pressure equalization mode on-off valve 16 is opened while maintaining the connected state in the heating mode, so that the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is set to be smaller at the start of the defrosting mode than at the end of the heating mode. Since the flow path resistance of on-off valve 16 is greater than the flow path resistance of four-way valve 15, the amount of refrigerant flowing out of heat exchanger 12 in the pressure equalization mode can be reduced.
  • the differential pressure between the pressure on the high pressure side and the pressure on the low pressure side can be set to be smaller at the start of the defrosting mode than at the end of the heating mode.
  • the pressure equalization mode is adopted before the defrosting mode, so that the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is set to be smaller at the start of the defrosting mode than at the end of the heating mode.
  • Fig. 3 is a flowchart illustrating the flow of the process in which controller 17 in Fig. 1 switches the operation mode of refrigeration cycle apparatus 1.
  • a step will be simply referred to as S.
  • the process shown in Fig. 3 is performed through a main routine (not shown) through which refrigeration cycle apparatus 1 is comprehensively controlled.
  • controller 17 determines in S10 whether the termination condition for refrigeration cycle apparatus 1 is satisfied or not.
  • the termination condition for refrigeration cycle apparatus 1 may be the condition that the termination operation has been performed by a user, or the condition that the termination time set by the user has arrived.
  • controller 17 returns the process to a main routine.
  • controller 17 causes the process to proceed to S20.
  • Controller 17 adopts a heating mode in S20. When the defrosting start condition is satisfied in the heating mode, controller 17 causes the process to proceed to S200.
  • Examples of the defrosting start condition may be the condition that the temperature in heat exchanger 14 is lower than a reference temperature, or the condition that the amount of frost formed (amount of formed frost) on heat exchanger 14 has exceeded a reference amount.
  • the amount of formed frost can be calculated from the temperature in heat exchanger 14 and the humidity around heat exchanger 14.
  • controller 17 After adopting the pressure equalization mode in S200, controller 17 causes the process to proceed to S300. After adopting the defrosting mode in S300, controller 17 returns the process to S10. Controller 17 switches the operation mode in order of the heating mode (S20), the pressure equalization mode (S200), and the defrosting mode (S300).
  • Fig. 4 is a diagram showing the function configuration of refrigeration cycle apparatus 1 in Fig. 1 , together with the flow of refrigerant in the pressure equalization mode.
  • controller 17 stops compressor 11, closes expansion valve 13, and opens on-off valve 16.
  • four-way valve 15 serves to maintain the connection between the discharge port of compressor 11 and heat exchanger 12 in the heating mode, and also, maintain the connection between heat exchanger 14 and the suction port of compressor 11 in the heating mode. Since expansion valve 13 is closed, the refrigerant is prevented from flowing from heat exchanger 12 with high pressure refrigerant through expansion valve 13 to heat exchanger 14 with low pressure refrigerant.
  • the refrigerant flows from heat exchanger 12 through on-off valve 16 into heat exchanger 14.
  • the flow path resistance of on-off valve 16 is higher than the flow path resistance of four-way valve 15. Accordingly, the amount of refrigerant flowing out of heat exchanger 12 in the pressure equalization mode is smaller than the amount of refrigerant flowing out of heat exchanger 12 when the defrosting mode is started without adopting the pressure equalization mode.
  • the differential pressure between the pressure on the high pressure side and the pressure on the low pressure side can be set to be smaller at the start of the defrosting mode than at the end of the heating mode. As a result, it becomes possible to suppress a temperature decrease in heat exchanger 12 at the start of the defrosting mode adopted after the pressure equalization mode.
  • Fig. 5 is a flowchart illustrating the flow of a process performed by controller 17 in Fig. 1 in the pressure equalization mode. The process shown in Fig. 5 is the same as the process performed in S200 in Fig. 3 .
  • controller 17 stops compressor 11 in S201, and then, causes the process to proceed to S202. Controller 17 closes expansion valve 13 in S202, and then, causes the process to proceed to S203. Controller 17 opens on-off valve 16 in S203, and then, causes the process to proceed to S204.
  • controller 17 determines whether the differential pressure between the discharge pressure and the suction pressure is smaller than a reference differential pressure or not. When the differential pressure between the discharge pressure and the suction pressure is smaller than the reference differential pressure (YES in S204), controller 17 determines that the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is sufficiently decreased. Then, controller 17 returns the process to a main routine.
  • controller 17 When the differential pressure between the discharge pressure and the suction pressure is equal to or greater than the reference differential pressure (NO in S204), controller 17 causes the process to proceed to S205.
  • controller 17 determines whether or not the reference time period has elapsed since on-off valve 16 was opened. When the reference time period has elapsed since on-off valve 16 was opened (YES in S205), controller 17 determines that pressure equalization between the refrigerant on the high pressure side and the refrigerant on the low pressure side has been sufficiently achieved. Then, controller 17 returns the process to the main routine.
  • controller 17 waits for a prescribed time period in S206, and then, returns the process to S204.
  • the reference differential pressure in S204 and the reference time period in S205 can be calculated as appropriate by a real machine experiment or through a simulation.
  • Fig. 6 is a flowchart illustrating the flow of the process performed by controller 17 in Fig. 1 in the defrosting mode. The process shown in Fig. 6 is the same as the process performed in S300 in Fig. 3 .
  • controller 17 switches four-way valve 15 in S301, and then, causes the process to proceed to S302.
  • controller 17 closes on-off valve 16, and then, causes the process to proceed to S303.
  • controller 17 opens expansion valve 13 to an appropriate degree of opening, and then, causes the process to proceed to S304.
  • controller 17 starts compressor 11, and then, causes the process to proceed to S305.
  • controller 17 determines whether a defrosting termination condition is satisfied or not. When the defrosting termination condition is satisfied (YES in S305), controller 17 returns the process to a main routine.
  • controller 17 waits for a prescribed time period in S306, and then, returns the process to S305.
  • the defrosting termination condition includes, for example, the condition that the temperature in heat exchanger 14 has become equal to or higher than the reference temperature, or the condition that the reference time period has elapsed since the defrosting mode was started.
  • heat exchanger 12 is lower in height than four-way valve 15. Furthermore, the height of a connection portion J10 between: the flow path connecting the suction port of compressor 11 and four-way valve 15; and the flow path through which the refrigerant from on-off valve 16 flows is lower than the height of four-way valve 15. Thus, the refrigerant is less likely to flow from heat exchanger 12 to four-way valve 15. Also, the refrigerant is less likely to flow from connection portion J10 to four-way valve 15. As a result, the amount of refrigerant flowing out of heat exchanger 12 in the pressure equalization mode can be further reduced.
  • Fig. 7 is an enlarged view of connection portion J10 and therearound shown in Fig. 4 , connection portion J10 being provided between: a flow path RP1 connecting the suction port of compressor 11 and four-way valve 15; and a flow path RP2 through which the refrigerant from on-off valve 16 flows.
  • an angle ⁇ 1 formed between flow paths RP1 and RP2 is greater than 0 degree and less than 180 degrees. Accordingly, the refrigerant flowing through flow path RP2 collides with the inner wall of flow path RP1 in connection portion J10 between flow paths RP1 and RP2.
  • the refrigerant from on-off valve 16 is less likely to merge into flow path RP1, to thereby decrease the amount of refrigerant per unit time that flows through on-off valve 16 in the pressure equalization mode. As a result, it becomes possible to further reduce the amount of the refrigerant flowing out of heat exchanger 12 in the pressure equalization mode.
  • flow path RP2 is narrower than flow path RP1 as shown in Fig. 7 .
  • flow path RP1 has a cross section that is orthogonal to the flowing direction of the refrigerant flowing through flow path RP1 and flow path RP2 has a cross section that is orthogonal to the flowing direction of the refrigerant that flows through flow path RP2.
  • the area of the cross section of flow path RP2 through which the refrigerant flows is smaller than the area of the cross section of flow path RP1 through which the refrigerant flows.
  • the amount of refrigerant flowing per unit time through on-off valve 16 in the pressure equalization mode can be reduced as compared with the case where flow path RP2 is equal in thickness to flow path RP1.
  • the amount of refrigerant flowing out of heat exchanger 12 can be further reduced.
  • the manufacturing cost of refrigeration cycle apparatus 1 can be suppressed as compared with the case where flow path RP2 is equal in thickness to flow path RP1.
  • the pressure equalization mode is adopted before the defrosting mode, which can suppress a temperature decrease at the start of the defrosting mode in the heat exchanger that has been functioning as a condenser in the heating mode.
  • the refrigeration cycle apparatus can be stably operated.
  • the first reference arrangement has been described with regard to the case where the on-off valve that is opened in the pressure equalization mode is closed before the compressor is started in the defrosting mode.
  • the first embodiment will be described below with regard to the case where the on-off valve is closed after the compressor is started in the defrosting mode.
  • the compressor is operated while the on-off valve is kept opened for a certain time period after the start of the defrosting mode. While the on-off valve is kept opened, a part of the refrigerant that is discharged from the compressor is returned through the on-off valve to the suction port of the compressor.
  • the refrigerant from the heat exchanger that has been functioning as a condenser in the heating mode is less likely to be suctioned into the compressor by the amount of the refrigerant that has been returned to the suction port of the compressor through the on-off valve.
  • the amount of refrigerant flowing out of the heat exchanger at the start of the defrosting mode can be further reduced.
  • the first embodiment is different in the process flow in the defrosting mode from the first reference arrangement. Except for the above, the first embodiment is the same as the first reference arrangement. Specifically, Figs. 2 and 6 of the first reference arrangement are replaced with Figs. 8 and 9 , respectively, of the first embodiment. Since the configurations other than the above are the same, the description thereof will not be repeated.
  • Fig. 8 is a diagram showing the function configuration of a refrigeration cycle apparatus 2 according to the first embodiment, together with the flow of refrigerant at the start of the defrosting mode.
  • on-off valve 16 is opened at the start of the defrosting mode of refrigeration cycle apparatus 2. While the on-off valve is opened, a part of the refrigerant that has been discharged from compressor 11 is returned through on-off valve 16 into the suction port of compressor 11.
  • Fig. 9 is a flowchart illustrating the flow of the process performed by controller 17 in Fig. 8 in the defrosting mode.
  • controller 17 switches four-way valve 15 in S311, and then, causes the process to proceed to S312.
  • controller 17 opens expansion valve 13 to an appropriate degree of opening, and then, causes the process to proceed to S313.
  • controller 17 starts compressor 11 and causes the process to proceed to S314.
  • controller 17 determines whether the defrosting termination condition is satisfied or not.
  • controller 17 causes the process to proceed to S315.
  • controller 17 determines whether on-off valve 16 is opened or not.
  • controller 17 When on-off valve 16 is closed (NO in S315), controller 17 returns the process to a main routine.
  • controller 17 closes on-off valve 16 in S316, and then, returns the process to a main routine.
  • controller 17 causes the process to proceed to S317.
  • controller 17 determines whether the suction pressure exceeds the reference pressure or not. When the suction pressure exceeds the reference pressure (YES in S317), controller 17 determines that the suction pressure has sufficiently increased. Thus, controller 17 closes on-off valve 16 in S319 and waits for a prescribed time period in S320. Then, controller 17 returns the process to S314.
  • controller 17 determines whether the reference time period has elapsed or not since compressor 11 was started.
  • controller 17 determines that a time period sufficient to increase the suction pressure has elapsed. Thus, controller 17 closes on-off valve 16 in S319. Then, after controller 17 waits for a prescribed time period in S320, it returns the process to S314. When the reference time period has not elapsed since compressor 11 was started (NO in S318), the controller returns the process to S314.
  • the reference pressure in S317 and the reference time period in S318 can be calculated as appropriate by a real machine experiment or through a simulation.
  • the pressure equalization mode is adopted before the defrosting mode, which can suppress a temperature decrease at the start of the defrosting mode in the heat exchanger that has been functioning as a condenser in the heating mode. As a result, the refrigeration cycle apparatus can be stably operated.
  • the compressor is operated while the on-off valve is kept opened for a certain time period after the start of the defrosting mode.
  • the first embodiment has been described with regard to the case where the pressure equalization mode is adopted after the heating mode when the defrosting start condition is satisfied.
  • the second embodiment will be hereinafter described with regard to the case where, when the defrosting start condition is satisfied, the heating mode is adopted, which is followed by the pump down mode, which is followed by the pressure equalization mode.
  • the pump down mode the amount of refrigerant inside the heat exchanger that has been functioning as a condenser in the heating mode is increased.
  • the pump down mode is adopted before the pressure equalization mode, so that the amount of refrigerant inside the heat exchanger at the start of the pressure equalization mode becomes greater than that in the first embodiment.
  • the refrigeration cycle apparatus can be further stably operated.
  • the second embodiment is different from the first embodiment in that a pump down mode is added to the operation mode.
  • Fig. 3 in the first embodiment is replaced with Fig. 10 in the second embodiment. Since the features other than the above are the same, the description thereof will not be repeated.
  • Fig. 10 is a flowchart illustrating the flow of the process in which a controller of a refrigeration cycle apparatus according to the second embodiment switches the operation mode of the refrigeration cycle apparatus.
  • the controller when the defrosting start condition is satisfied in the heating mode (S20), the controller adopts the pump down mode in S100. Then, in the same manner as in the first embodiment, the controller adopts the pressure equalization mode in S200, and adopts the defrosting mode in S300.
  • the controller switches the operation mode in order of the heating mode, the pump down mode, the pressure equalization mode, and the defrosting mode.
  • Fig. 11 is a diagram showing the function configuration of a refrigeration cycle apparatus 3 according to the second embodiment, together with the flow of refrigerant in the pump down mode.
  • controller 17 causes compressor 11 to operate, closes expansion valve 13, and closes on-off valve 16.
  • four-way valve 15 serves to maintain the connection between the discharge port of compressor 11 and heat exchanger 12, and also maintain the connection between heat exchanger 14 and the suction port of compressor 11. Since compressor 11 is operated while expansion valve 13 is closed, the refrigerant discharged from compressor 11 is stored in heat exchanger 12. While the pump down mode is adopted, the amount of refrigerant inside heat exchanger 12 increases.
  • the amount of refrigerant inside heat exchanger 12 at the start of the pressure equalization mode is greater than that in the first embodiment in which the pump down mode is not adopted.
  • the amount of refrigerant remaining inside heat exchanger 12 is greater than that in the first embodiment. Accordingly, a temperature decrease in heat exchanger 12 can be suppressed as compared with the first embodiment.
  • Fig. 12 is a flowchart illustrating the flow of the process performed by controller 17 in Fig. 11 in the pump down mode.
  • the process shown in Fig. 12 is the same as the process performed in S100 in Fig. 10 .
  • controller 17 closes expansion valve 13 in S101, and then, causes the process to proceed to S102. Controller 17 determines in S102 whether the suction pressure is smaller than the reference pressure or not. When the suction pressure is smaller than the reference pressure (YES in S102), controller 17 determines that the amount of refrigerant suctioned into compressor 11 has decreased due to a sufficient amount of refrigerant stored in heat exchanger 12, and then, returns the process to a main routine. When the suction pressure is equal to or greater than the reference pressure (NO in S102), controller 17 causes the process to proceed to S103. In S103, controller 17 determines whether the reference time period has elapsed or not since expansion valve 13 was closed.
  • controller 17 determines that a time period sufficient to increase the amount of refrigerant inside heat exchanger 12 has elapsed, and then, returns the process to a main routine.
  • controller 17 waits for a prescribed time period in S104, and then, returns the process to S102.
  • the heat capacity of the heat exchanger in the defrosting mode is increased.
  • the amount of the refrigerant that flows into the heat exchanger at the start of the defrosting mode is increased.
  • the amount of formed frost is increased, the amount of refrigerant flowing out, at the start of the defrosting mode, from the heat exchanger that has been functioning as a condenser in the heating mode is increased.
  • the amount of formed frost when the amount of formed frost is relatively small, the amount of refrigerant flowing out, at the start of the defrosting mode, from the heat exchanger that has been functioning as a condenser in the heating mode is decreased.
  • the amount of formed frost when the amount of formed frost is relatively small, it is desirable to shorten the time period of the pump down mode in order to shorten the downtime of the heating mode.
  • the reference time period in S103 in Fig. 12 may be shortened by a prescribed proportion (S40).
  • the amount of formed frost may be determined depending on the amount of formed frost whether to adopt the pump down mode or not. For example, as in the process shown in Fig. 15 , when the amount of formed frost is smaller than the reference amount (YES in S30), the pressure equalization mode (S200) may be adopted without adopting the pump down mode. By performing the process as shown in Fig. 15 , an unnecessary pump down mode can be avoided. As a result, the downtime of the heating mode can be shortened.
  • the first modification and the second modification by adopting a pressure equalization mode before a defrosting mode, it becomes possible to suppress a temperature decrease in the heat exchanger that has been functioning as a condenser in the heating mode at the start of the defrosting mode. As a result, the refrigeration cycle apparatus can be stably operated.
  • the first modification and the second modification by adopting the pump down mode before the pressure equalization mode, the amount of refrigerant inside the heat exchanger that has been functioning as a condenser in the heating mode is increased before the pressure equalization mode is adopted.
  • a temperature decrease at the start of the defrosting mode in the heat exchanger can be further suppressed.
  • the refrigeration cycle apparatus can be further stably operated.
  • the third embodiment is different from the first embodiment in the following points.
  • the four-way valve can be operated when the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is equal to or greater than the reference differential pressure, and also, a differential pressure regulating valve for maintaining the differential pressure to be equal to or greater than the reference differential pressure is provided. Since the configurations other than the above are the same, the description thereof will not be repeated.
  • Fig. 16 is a diagram showing the function configuration of a refrigeration cycle apparatus 4 according to the third embodiment, together with the flow of refrigerant in the pressure equalization mode.
  • four-way valve 15 of refrigeration cycle apparatus 1 shown in Fig. 4 is replaced with a four-way valve 154.
  • Four-way valve 154 can be operated when the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is equal to or greater than the reference differential pressure.
  • refrigeration cycle apparatus 4 further includes a differential pressure regulating valve 40 in addition to the configuration of refrigeration cycle apparatus 1 shown in Fig. 4 .
  • Differential pressure regulating valve 40 is connected in series to on-off valve 16 between the discharge port and the suction port of compressor 11. Differential pressure regulating valve 40 serves as a mechanical valve for maintaining the pressure difference between both ends of differential pressure regulating valve 40 to be equal to or greater than the reference differential pressure.
  • differential pressure regulating valve 40 In refrigeration cycle apparatus 4, the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is maintained by differential pressure regulating valve 40 to be equal to or greater than the reference differential pressure.
  • the configuration capable of setting the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side to be equal to or greater than the reference differential pressure is not limited to a differential pressure regulating valve.
  • a valve 41 for which the degree of opening can be adjusted in a stepwise manner in its opened state may be employed in place of on-off valve 16.
  • the degree of opening of valve 41 may be adjusted by controller 17 such that the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side becomes equal to or greater than the reference differential pressure.
  • the refrigeration cycle apparatus As described above, also in the refrigeration cycle apparatus according to each of the third embodiment and the modification, by adopting the pressure equalization mode before the defrosting mode, it becomes possible to suppress a temperature decrease in the heat exchanger that has been functioning as a condenser in the heating mode at the start of the defrosting mode. As a result, the refrigeration cycle apparatus can be stably operated.
  • the refrigeration cycle apparatus of each of the third embodiment and the modification it becomes possible to prevent occurrence of the situation where the flow path switching device cannot be operated because the differential pressure between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is smaller than the reference differential pressure. As a result, the refrigeration cycle apparatus can be further stably operated.
  • the fourth embodiment will be hereinafter described with regard to the case where a gas-liquid separator is connected between the on-off valve and the suction port of the compressor.
  • the refrigerant flowing out, in the pressure equalization mode, from the heat exchanger that has been functioning as a condenser in the heating mode is stored in the gas-liquid separator in the pressure equalization mode.
  • the refrigerant from the gas-liquid separator is also supplied in addition to the refrigerant from the heat exchanger that has been functioning as a condenser in the heating mode.
  • the amount of the refrigerant flowing out of the heat exchanger at the start of the defrosting mode can be reduced as compared with that in the first embodiment.
  • the flow path resistance of the on-off valve is set to be smaller than that in the first embodiment to thereby increase the amount of refrigerant flowing out of the heat exchanger that has been functioning as a condenser in the heating mode
  • the refrigerant from the heat exchanger is stored in the gas-liquid separator in the pressure equalization mode. Since the refrigerant from the gas-liquid separator is also added to the refrigerant suctioned into the compressor at the start of the defrosting mode, a temperature decrease in the heat exchanger that has been functioning as a condenser in the heating mode can be suppressed to the same degree as that in the first embodiment.
  • the flow path resistance of the on-off valve is set to be smaller than that in the first embodiment, the time period required for the pressure equalization mode can be shorter than that in the first embodiment. As a result, the downtime of the heating operation can be shortened.
  • Fig. 18 is a diagram showing the function configuration of a refrigeration cycle apparatus 5 according to the fourth embodiment, together with the flow of refrigerant in the pressure equalization mode.
  • refrigeration cycle apparatus 5 includes an on-off valve 165 in place of on-off valve 16 of refrigeration cycle apparatus 1 shown in Fig. 4 .
  • the flow path resistance of on-off valve 165 is greater than the flow path resistance of four-way valve 15 and smaller than the flow path resistance of on-off valve 165 in the state where on-off valve 165 is opened.
  • refrigeration cycle apparatus 5 further includes a gas-liquid separator 50 in addition to the configuration of refrigeration cycle apparatus 1 shown in Fig. 4 .
  • Gas-liquid separator 50 is connected between on-off valve 165 and the suction port of compressor 11.
  • Gas-liquid separator 50 includes a discharge port LS1 through which the stored liquid refrigerant is discharged.
  • Discharge port LS1 is connected to a junction point J2 of the flow path that connects the suction port of compressor 11 and four-way valve 15.
  • Discharge port LS1 is located lower in height than junction point J2.
  • the refrigerant that has flowed out of heat exchanger 12 in the pressure equalization mode passes through on-off valve 165, and after that, the refrigerant is stored in gas-liquid separator 50.
  • the liquid refrigerant stored in gas-liquid separator 50 is discharged through discharge port LS1 and merges at junction point J2 into the refrigerant that flows toward heat exchanger 14.
  • the refrigerant from heat exchanger 12 passes through on-off valve 165, and then, the refrigerant is stored in gas-liquid separator 50.
  • the refrigerant from gas-liquid separator 50 is also supplied in addition to the refrigerant from heat exchanger 12. Accordingly, the amount of the refrigerant flowing out of heat exchanger 12 at the start of the defrosting mode can be reduced.
  • the flow path resistance of on-off valve 165 is smaller than the flow path resistance of on-off valve 16 in the first embodiment, the time period required for the pressure equalization mode can be shorter than that in the first embodiment.
  • discharge port LS 1 is located lower in height than junction point J2
  • the amount of refrigerant discharged from gas-liquid separator 50 can be reduced.
  • the amount of refrigerant that flows from the high pressure side toward the low pressure side can be further reduced.
  • the refrigeration cycle apparatus by adopting the pressure equalization mode before the defrosting mode, it becomes possible to suppress a temperature decrease at the start of the defrosting mode in the heat exchanger that has been functioning as a condenser in the heating mode. As a result, the refrigeration cycle apparatus can be stably operated.
  • the refrigerant from the heat exchanger that has been functioning as a condenser in the heating mode is stored in the gas-liquid separator, so that it becomes possible to reduce the amount of the refrigerant flowing out, at the start of the defrosting mode, from the heat exchanger that has been functioning as a condenser in the heating mode. Furthermore, since the flow path resistance of the on-off valve can be set to be smaller than that in the first embodiment, the time period required for the pressure equalization mode can be shorter than that in the first embodiment.

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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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (12)

  1. Kühlzyklusvorrichtung (1), die ausgelegt ist, um in einem Betriebsmodus, einschließlich eines Erhitzungsmodus und eines Enteisungsmodus, zu arbeiten,
    wobei in dem Erhitzungsmodus Kühlmittel nacheinander durch einen Kompressor (11), eine Strömungspfadschaltvorrichtung (15), einen ersten Wärmetauscher (12), ein Entspannungsventil (13) und einen zweiten Wärmetauscher (14) zirkuliert und
    wobei in dem Enteisungsmodus das Kühlmittel nacheinander durch den Kompressor (11), die Strömungspfadschaltvorrichtung (15), den zweiten Wärmetauscher (14), das Entspannungsventil (13) und den ersten Wärmetauscher (12) zirkuliert,
    wobei die Kühlzyklusvorrichtung (1) Folgendes umfasst:
    ein Strömungsregulationsventil (16), das zwischen einem Ablassanschluss des Kompressors (11) und einem Ansauganschluss des Kompressors (11) parallel mit dem Kompressor (11) verbunden ist; und
    eine Steuerung (17), die ausgelegt ist, um einen Öffnungsgrad des Strömungsregulationsventils (16) zu steuern und den Betriebsmodus zu schalten, wobei
    der Betriebsmodus ferner einen Druckausgleichsmodus umfasst,
    wobei in dem Druckausgleichsmodus:
    das Strömungsregulationsventil (16) geöffnet ist und
    die Steuerung (17) ausgelegt ist, um den Betriebsmodus in der Reihenfolge von Erhitzungsmodus, Druckausgleichsmodus und Enteisungsmodus zu schalten,
    dadurch gekennzeichnet, dass:
    in dem Druckausgleichsmodus ein Strömungspfadwiderstand des Strömungsregulationsventils (16) größer ist als ein Strömungspfadwiderstand der Strömungspfadschaltvorrichtung (15), wobei der Strömungspfadwiderstand des Strömungsregulationsventils (16) proportional zum Öffnungsgrad ist,
    wobei die Strömungspfadschaltvorrichtung (15) ausgelegt ist, um einen Verbindungszustand der Kühlzyklusvorrichtung (1) zwischen einem ersten Verbindungszustand und einem zweiten Verbindungszustand zu schalten und
    die Steuerung (17) ausgelegt ist, um:
    in dem Erhitzungsmodus den Verbindungszustand auf den ersten Verbindungszustand einzustellen, zu bewirken, dass der Kompressor (11) arbeitet, das Entspannungsventil (13) zu öffnen und das Strömungsregulationsventil (16) zu schließen,
    in dem Druckausgleichsmodus den Verbindungszustand in dem ersten Verbindungszustand zu halten, den Kompressor (11) anzuhalten, das Entspannungsventil (13) zu schließen und den Öffnungsgrad des Strömungsregulationsventils (16) zu erhöhen und
    in dem Enteisungsmodus den Verbindungszustand auf den zweiten Verbindungszustand einzustellen, zu bewirken, dass der Kompressor (11) arbeitet, das Entspannungsventil (13) zu öffnen und das Strömungsregulationsventil (16) zu schließen und
    wobei die Steuerung (17) ausgelegt ist, um das Strömungsregulationsventil (16) nach dem Start des Kompressors (11) in dem Enteisungsmodus zu schließen.
  2. Kühlzyklusvorrichtung (3) nach Anspruch 1, wobei
    der Betriebsmodus ferner einen Abpumpmodus umfasst, in dem eine Menge des Kühlmittels im Inneren des ersten Wärmetauschers (12) erhöht wird, und
    die Steuerung (17) ausgelegt ist, um:
    den Betriebsmodus in der Reihenfolge von Erhitzungsmodus, Abpumpmodus, Druckausgleichsmodus und Enteisungsmodus zu schalten und
    in dem Abpumpmodus den Verbindungszustand in dem ersten Verbindungszustand zu halten, zu bewirken, dass der Kompressor (11) arbeitet, das Entspannungsventil (13) zu schließen und das Strömungsregulationsventil (16) zu schließen.
  3. Kühlzyklusvorrichtung (3) nach Anspruch 2, wobei die Steuerung (17) ausgelegt ist, um eine Betriebszeit des Abpumpmodus gemäß einer Menge von Frost, die sich auf dem zweiten Wärmetauscher (14) in dem Erhitzungsmodus gebildet hat, anzupassen.
  4. Kühlzyklusvorrichtung (3) nach Anspruch 1, wobei
    der Betriebsmodus ferner einen Abpumpmodus umfasst, in dem eine Menge von Kühlmittel im Inneren des ersten Wärmetauschers (12) erhöht wird, und
    die Steuerung (17) ausgelegt ist, um:
    den Betriebsmodus in der Reihenfolge von Erhitzungsmodus, Abpumpmodus, Druckausgleichsmodus und Enteisungsmodus zu schalten, wenn eine Menge von Frost, die sich auf dem zweiten Wärmetauscher (14) in dem Erhitzungsmodus gebildet hat, größer ist als eine Referenzmenge,
    den Betriebsmodus in der Reihenfolge von Erhitzungsmodus, Druckausgleichsmodus und Enteisungsmodus zu schalten, wenn die Menge von Frost, die sich in dem Erhitzungsmodus gebildet hat, kleiner ist als die Referenzmenge, und
    in dem Abpumpmodus den Verbindungszustand in dem ersten Verbindungszustand zu halten, zu bewirken, dass der Kompressor (11) arbeitet, das Entspannungsventil (13) zu schließen und das Strömungsregulationsventil (16) zu schließen.
  5. Kühlzyklusvorrichtung (3A) nach einem der Ansprüche 2 bis 4, ferner umfassend einen Kühlmittelsammelabschnitt (30), der zwischen dem ersten Wärmetauscher (12) und dem Entspannungsventil (13) angeordnet ist.
  6. Kühlzyklusvorrichtung (4) nach einem der Ansprüche 1 bis 5, wobei
    die Strömungspfadschaltvorrichtung (154) dazu in der Lage ist, den Verbindungszustand zu schalten, wenn ein Differenzdruck zwischen einem Druck des Kühlmittels aus dem Ablassanschluss an das Entspannungsventil (13) und ein Druck des Kühlmittels aus dem Entspannungsventil (13) an den Ansauganschluss größer oder gleich einem Referenzdifferenzdruck ist,
    die Kühlzyklusvorrichtung (4) ferner ein Differenzdruckregulationsventil (40) umfasst, das zwischen dem Ablassanschluss und dem Ansauganschluss mit dem Strömungsregulationsventil (16) in Reihe verbunden ist und
    wobei das Differenzdruckregulationsventil (40) ausgelegt ist, um den Differenzdruck so zu halten, dass er größer oder gleich dem Referenzdifferenzdruck ist.
  7. Kühlzyklusvorrichtung (4A) nach einem der Ansprüche 1 bis 5, wobei
    die Strömungspfadschaltvorrichtung (154) dazu in der Lage ist, den Verbindungszustand zu schalten, wenn ein Differenzdruck zwischen einem Druck des Kühlmittels aus dem Ablassanschluss an das Entspannungsventil (13) und einem Druck des Kühlmittels aus dem Entspannungsventil (13) an den Ansauganschluss größer oder gleich einem Referenzdifferenzdruck ist und
    die Steuerung (17) ausgelegt ist, um den Öffnungsgrad so anzupassen, dass der Differenzdruck größer oder gleich dem Referenzdifferenzdruck in dem Druckausgleichsmodus ist.
  8. Kühlzyklusvorrichtung (5) nach einem der Ansprüche 1 bis 7, ferner umfassend einen Gas/Flüssigkeit-Separator (50), der zwischen das Strömungsregulationsventil (165) und den Ansauganschluss geschaltet ist, wobei
    der Gas/Flüssigkeit-Separator (50) einen Flüssigkeitsablassanschluss (LS1) aufweist, durch den eine Flüssigkeit des gesammelten Kühlmittels abgelassen wird, und
    der Flüssigkeitsablassanschluss (LS1) mit einem Strömungspfad verbunden ist, der den Ansauganschluss und die Strömungspfadschaltvorrichtung (15) verbindet.
  9. Kühlzyklusvorrichtung (5) nach Anspruch 8, wobei der Flüssigkeitsablassanschluss (LS1) eine geringere Höhe aufweist als ein Übergangspunkt (J2), an dem die Flüssigkeit aus dem Flüssigkeitsablassanschluss (LS1) in den Strömungspfad einströmt.
  10. Kühlzyklusvorrichtung (1) nach Anspruch 1, wobei
    der erste Wärmetauscher (12) eine geringere Höhe aufweist als die Strömungspfadschaltvorrichtung (15),
    ein Verbindungsabschnitt zwischen einem ersten Strömungspfad und einem zweiten Strömungspfad eine geringere Höhe aufweist als die Strömungspfadschaltvorrichtung (15),
    der erste Strömungspfad den Ansauganschluss und die Strömungspfadschaltvorrichtung (15) verbindet und
    der zweite Strömungspfad mit dem ersten Strömungspfad verbunden ist und ermöglicht, dass das Kühlmittel aus dem Strömungsregulationsventil (16) durch ihn hindurch strömt.
  11. Kühlzyklusvorrichtung (1) nach Anspruch 1, wobei
    ein Winkel (α1), der zwischen einem ersten Strömungspfad (PR1) und einem zweiten Strömungspfad (PR2) gebildet wird, in einem Verbindungsabschnitt (J10) zwischen dem ersten Strömungspfad (PR1) und dem zweiten Strömungspfad (PR2) größer als 0 Grad und kleiner als 180 Grad ist,
    der erste Strömungspfad (PR1) den Ansauganschluss und die Strömungspfadschaltvorrichtung (15) verbindet und
    der zweite Strömungspfad (PR2) mit dem ersten Strömungspfad (PR1) verbunden ist und ermöglicht, dass das Kühlmittel aus dem Strömungsregulationsventil (16) durch ihn hindurch strömt.
  12. Kühlzyklusvorrichtung (1) nach Anspruch 1, wobei
    ein erster Strömungspfad (PR2) einen Querschnitt aufweist, der orthogonal zu einer Strömungsrichtung des Kühlmittels ist, das durch den ersten Strömungspfad (PR2) strömt, der mit dem Strömungsregulationsventil (16) verbunden ist,
    ein zweiter Strömungspfad (PR1) einen Querschnitt aufweist, der orthogonal zu einer Strömungsrichtung des Kühlmittels ist, das durch den zweiten Strömungspfad (PR1) strömt, der mit dem Ansauganschluss verbunden ist, und
    eine Fläche des Querschnitts des ersten Strömungspfads (PR2), durch den das Kühlmittel strömt, kleiner ist als eine Fläche des Querschnitts des zweiten Strömungspfads (PR1), durch den das Kühlmittel strömt.
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