EP2623898A1 - Système d'alimentation en eau chaude - Google Patents

Système d'alimentation en eau chaude Download PDF

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Publication number
EP2623898A1
EP2623898A1 EP11828854.7A EP11828854A EP2623898A1 EP 2623898 A1 EP2623898 A1 EP 2623898A1 EP 11828854 A EP11828854 A EP 11828854A EP 2623898 A1 EP2623898 A1 EP 2623898A1
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EP
European Patent Office
Prior art keywords
temperature
refrigeration cycle
low
heat exchanger
temperature refrigeration
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.)
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Application number
EP11828854.7A
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German (de)
English (en)
Other versions
EP2623898A4 (fr
Inventor
Takahiro Zushi
Shun Asari
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Application filed by Toshiba Carrier Corp filed Critical Toshiba Carrier Corp
Publication of EP2623898A1 publication Critical patent/EP2623898A1/fr
Publication of EP2623898A4 publication Critical patent/EP2623898A4/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
    • F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • 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
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • Embodiments described herein relate generally to a hot water supply system that supplies hot water by using a cascade refrigeration cycle.
  • a cascade refrigeration cycle to obtain a high compression ratio by connecting a high-temperature refrigeration cycle and a low-temperature refrigeration cycle via an intermediate heat exchanger and causing the intermediate heat exchanger to exchange heat of a refrigerant circulating through the high-temperature refrigeration cycle and a refrigerant circulating through the low-temperature refrigeration cycle tends to be used more frequently (for example, Jpn. Pat. Appln. KOKAI Publication No. 2000-320914 ).
  • a water heat exchanger is included as a condenser constituting the high-temperature refrigeration cycle and water or hot water is guided thereto via a hot water pipe.
  • the water or hot water is exchanged for high-temperature hot water, which is supplied to the side of use to which the hot water pipe is connected. Therefore, an efficient hot water supply operation can be performed even in a cold district.
  • a four-way valve of the high-temperature refrigeration cycle and a four-way valve of the low-temperature refrigeration cycle are switched in the reverse direction to reverse the circulation direction of the refrigerant.
  • Hot water guided into the water heat exchanger of the high-temperature refrigeration cycle is used as a heat source for defrosting and thus, a high pressure and a discharge temperature during defrosting operation can be maintained. Because a high-temperature gas refrigerant is directly guided into the aero-thermal exchanger of the low-temperature refrigeration cycle, the aero-thermal exchanger can be defrosted efficiently.
  • the four-way valve is expensive and if possible, the cost should be reduced through the reduction of parts costs by removing the four-way valve and pipes connected to the four-way valve.
  • the present embodiment has been made based on the above circumstances and a hot water supply system capable of reducing parts costs and performing an efficient defrosting operation by including the cascade refrigeration cycle and exercising special control for defrosting operation of an evaporator of the low-temperature refrigeration cycle is provided.
  • a hot water supply system of the present invention comprises, a cascade refrigeration cycle constituted of a low-temperature refrigeration cycle communicatively connecting a low-temperature compressor, a four-way valve, an intermediate heat exchanger, a low-temperature expansion device, and an evaporator via a refrigerant pipe and a high-temperature refrigeration cycle communicatively connecting a high-temperature compressor, a water heat exchanger, a high-temperature expansion device, and the intermediate heat exchanger via the refrigerant pipe to cause the intermediate heat exchanger to exchange heat of a refrigerant guided to the low-temperature refrigeration cycle and a refrigerant guided to the high-temperature refrigeration cycle, a hot water pipe communicating with the water heat exchanger in the high-temperature refrigeration cycle to cause circulating water or hot water and the refrigerant guided to the high-temperature refrigeration cycle to exchange heat and to supply the heat to a side of use, a bypass circuit whose one end is connected to the refrigerant pipe between
  • FIG. 1 is a block diagram of a refrigeration cycle of a hot water supply system and shows particularly a refrigeration cycle switchover state during defrosting operation.
  • the hot water supply system is constituted of a high-temperature refrigeration cycle Ra, a hot water pipe H, a low-temperature refrigeration cycle Rb, and a controller (control unit) S.
  • the high-temperature refrigeration cycle Ra will first be described.
  • a discharge portion a of a high-temperature compressor 1, a water heat exchanger 2, a liquid receiver 3, a high-temperature expansion device 4, a heat sink 5a of an intermediate heat exchanger 5, and a gas liquid separation device 6 are connected in succession via a refrigerant pipe P and the gas liquid separation device 6 is communicatively connected to a suction portion b of the high-temperature compressor 1.
  • a refrigerant compressed and discharged by the high-temperature compressor 1 is guided in the sequence of water heat exchanger 2 ⁇ liquid receiver 3 ⁇ high-temperature expansion device 4 ⁇ heat sink 5a of intermediate heat exchanger 5 ⁇ gas liquid separation device 6 ⁇ high-temperature compressor 1.
  • the water heat exchanger 2 acts as a condenser and the heat sink 5a of the intermediate heat exchanger 5 acts as an evaporator.
  • a bypass circuit B is provided in the high-temperature refrigeration cycle Ra.
  • the bypass circuit B is formed of a bypass pipe 9 whose one end is connected to the refrigerant pipe P between the discharge portion a of the high-temperature compressor 1 and the water heat exchanger 2, whose other end is connected to a refrigerant pipe P between the high-temperature expansion device 4 and the heat sink 5a of the intermediate heat exchanger 5, and having a fluid-controlled valve 8 in an intermediate portion.
  • the hot water pipe H has one end portion connected to a hot water return pipe or a return buffer tank and the other end portion connected to a hot water outlet pipe or a supply buffer tank (none of the above is illustrated).
  • the intermediate portion of the hot water pipe H communicates with the water heat exchanger 2 constituting the high-temperature refrigeration cycle Ra so that water or hot water guided into the hot water pipe H and a refrigerant guided into the water heat exchanger 2 can exchange heat.
  • a discharge portion c of a low-temperature compressor 10 and a first port d1 of a four-way valve 11 are connected via the refrigerant pipe P and a radiating portion 5b of the intermediate heat exchanger 5 is connected to a second port d2 of the four-way valve 11 via the refrigerant pipe P.
  • a third port d3 of the four-way valve 11 is connected to two aero-thermal exchanger 12, 12 via the refrigerant pipe P divided into two pipes in an intermediate portion thereof.
  • a fourth port d4 of the four-way valve 11 is connected to a suction portion e of the low-temperature compressor 10 via the refrigerant pipe P through a gas liquid separation device 13.
  • the radiating portion 5b of the intermediate heat exchanger 5 is connected to a liquid receiver 14 via the refrigerant pipe P and the liquid receiver 14 and the two aero-thermal exchangers 12 are connected via the refrigerant pipe P divided into two pipes in an intermediate portion, each of which having a low-temperature expansion device 15.
  • a refrigerant compressed and discharged by the low-temperature compressor 10 is guided in the sequence of four-way valve 11 ⁇ radiating portion 5b of intermediate heat exchanger 5 ⁇ liquid receiver 14 ⁇ two low-temperature expansion devices 15 ⁇ two aero-thermal exchangers 12 ⁇ four-way valve 11 ⁇ liquid separation device 13 ⁇ low-temperature compressor 10.
  • the radiating portion 5b of the intermediate heat exchanger 5 acts as a condenser and the aero-thermal exchanger 12 acts as an evaporator.
  • the four-way valve 11 is switched to the direction shown in FIG. 11 and a refrigerant compressed and discharged by the low-temperature compressor 10 is guided in the sequence of four-way valve 11 ⁇ two aero-thermal exchangers 12 ⁇ two low-temperature expansion devices 15 ⁇ liquid receiver 14 ⁇ radiating portion 5b of intermediate heat exchanger 5 ⁇ four-way valve 11 ⁇ liquid separation device 13 ⁇ low-temperature compressor 10.
  • the aero-thermal exchanger 12 acts as a condenser and the radiating portion of the intermediate heat exchanger 5 acts as an evaporator.
  • the controller S receives a detection signal from temperature sensors provided in the discharge portions a, c and the suction portions b, e of the high-temperature compressor 1 and the low-temperature compressor 10 respectively, pressure sensors provided in the discharge portions a, c and the suction portions b, e, a temperature sensor provided in the water heat exchanger 2, temperature sensors provided in the heat sink 5a and the radiating portion 5b of the intermediate heat exchanger 5, a temperature sensor (none of the sensors is illustrated) provided in the aero-thermal exchanger 12 and the like.
  • controller S performs an operation after receiving an instruction signal from a remote controller (remocon) and compares the operation result with a stored reference value (thermal capability, the temperature of the intermediate heat exchanger 5 and the like) to control the operating frequency of the high-temperature compressor 1 and the low-temperature compressor 10.
  • a remote controller remote controller
  • a stored reference value thermo capability, the temperature of the intermediate heat exchanger 5 and the like
  • the controller S calculates a superheat amount (hereinafter, referred to as an "SH amount") of a heat exchanger from a difference between a refrigerant temperature of the heat exchanger and a refrigerant temperature on the suction side of a compressor to control the throttling amount of the high-temperature expansion device 4 and the low-temperature expansion device 15. Then, the controller S executes control to open or close the fluid-controlled valve 8 of the bypass circuit B.
  • SH amount superheat amount
  • the hot water supply system is configured as described above and the controller S during hot water supply operation controls the high-temperature refrigeration cycle Ra and the low-temperature refrigeration cycle Rb so that the refrigerant is guided and circulated as described above.
  • the refrigerant is compressed by the radiating portion 5b on the side of the low-temperature refrigeration cycle Rb to give off heat of condensation and the refrigerant is evaporated by the heat sink 5a on the side of the high-temperature refrigeration cycle Ra while the heat of condensation being absorbed.
  • the difference of temperature between the evaporating temperature in the aero-thermal exchanger 12 and the condensing temperature in the water heat exchanger 2 increases in the hot water supply system as a whole so that a high compression ratio can be obtained.
  • water heat exchanger 2 executing a condensation function in the high-temperature refrigeration cycle Ra water or hot water guided into the hot water pipe H absorbs high heat of condensation and the temperature thereof rises efficiently.
  • the water or hot water is exchanged for high-temperature hot water in the water heat exchanger 2 and circulated by way of water heat exchanger 2 ⁇ supply buffer tank of hot water ⁇ return buffer-tank on load sidle ⁇ water heat exchanger 2.
  • the aero-thermal exchanger 12 in the low-temperature refrigeration cycle Rb executes an evaporation function and thus, condensed water generated here is frozen to form frost, which adheres to the aero-thermal exchanger 12.
  • the thickness of frost increases with the passage of time, decreasing the heat exchange efficiency by the aero-thermal exchanger 12.
  • the controller S receives not only a detection signal from the temperature sensor attached to the aero-thermal exchanger 12, but also a detection signal from other sensors to determine whether a defrosting operation of the aero-thermal exchanger 12 is needed.
  • the defrosting operation is performed based on the result of the determination and actually, the controller S exercises the control described below immediately before starting a defrosting operation.
  • the controller S exercises throttling control of the high-temperature expansion device 4 provided in the high-temperature refrigeration cycle Ra in the timing immediately before starting a defrosting operation.
  • the flow rate of the refrigerant guided from the high-temperature expansion device 4 into the heat sink 5a of the intermediate heat exchanger 5 decreases in the high-temperature refrigeration cycle Ra.
  • the amount of absorbed heat by the heat sink 5a of the intermediate heat exchanger 5 decreases and the temperatures of the heat sink 5a and the radiating portion 5b rise and also the temperature of the intermediate heat exchanger 5 as a whole rises. At this point, there is no need to change the operating frequency of the high-temperature compressor 1 in the high-temperature refrigeration cycle Ra and the low-temperature compressor 10 in the low-temperature refrigeration cycle Rb.
  • the suction temperature and suction pressure of the high-temperature compressor 1 communicatively connected via the heat sink 5a of the intermediate heat exchanger 5 and the refrigerant pipe P also rise, but the circulating amount of refrigerant in the high-temperature refrigeration cycle Ra decreases and thus, the discharge pressure hardly rises, leading to a lower compression ratio of the high-temperature compressor 1.
  • the suction temperature of the high-temperature compressor 1 rises and a difference from the evaporating temperature of the heat sink 5a of the intermediate heat exchanger executing an evaporation function increases and thus, the so-called SH amount becomes excessive and the discharge temperature of the high-temperature compressor 1 rises.
  • the low-temperature refrigeration cycle Rb with the rise in temperature of the radiating portion 5b of the intermediate heat exchanger, the compression ratio increases and the discharge temperature of the low-temperature compressor 10 rises.
  • the controller S exercises, as described above, throttling control of the high-temperature expansion device 4 of the high-temperature refrigeration cycle Ra in the timing immediately before starting a defrosting operation of the aero-thermal exchanger 12. Therefore, the rise in evaporating temperature of the heat sink 5a of the intermediate heat exchanger 5, the rise in condensing temperature of the radiating portion 5b, and the rise in discharge temperature of the high-temperature compressor 1 and the low-temperature compressor 10 are obtained in a short time without changing the operating frequency of the high-temperature compressor 1 and the low-temperature compressor 10.
  • the temperature of low-pressure piping parts ranging from the high-temperature expansion device 4 to the high-temperature compressor 1 via the intermediate heat exchanger 5 rises and also the temperature of the compressor body of the high-temperature compressor 1 and high-pressure piping parts ranging from the high-temperature compressor 1 to the water heat exchanger 2 rises so that heat can be stored.
  • the temperature of high-pressure piping parts ranging from the high-temperature compressor 1 and the low-temperature compressor 10 to the low-temperature expansion device 15 via the four-way valve 11 and the intermediate heat exchanger 5 rises so that heat can be stored.
  • the controller S controls the start of an actual defrosting operation of the aero-thermal exchanger 12.
  • the fluid-controlled valve 8 of the bypass circuit B is opened and the also the four-way valve 11 of the low-temperature refrigeration cycle Rb is switched to cause the refrigerant to circulate in the direction opposite to the refrigerant circulation direction heretofore.
  • the controller S stops the operation of the low-temperature compressor 10 once (a few tens of seconds to a few minutes) and also exercises necessary control such as opening an equalizing pipe to balance the pressure on the high-pressure side and the low-pressure side in the low-temperature refrigeration cycle Rb. Then, the flow of the refrigerant inside the switching valve is decreased by switching the four-way valve 11 so that switching noise can be inhibited by quieting the collision.
  • the controller S totally closes the high-temperature expansion device 4 while continuing the operation of the high-temperature compressor 1 in the high-temperature refrigeration cycle Ra.
  • the high pressure of the high-temperature refrigeration cycle Ra is maintained and the refrigerant recovered from the heat sink 5a of the intermediate heat exchanger 5 and discharged from the high-temperature compressor 1 stores heat by remaining in the water heat exchanger 2 as a condenser and the liquid receiver 3 as a high-temperature liquid refrigerant.
  • the amount of absorbed heat from the heat sink 5a can be restrained by the refrigerant not being supplied to the intermediate heat exchanger 5 so that a heat storage effect can be maintained.
  • a pump-down (refrigerant recovery) operation is performed in the high-temperature refrigeration cycle Ra and thus, it is desirable to extend the operation duration by reducing the operating frequency of the high-temperature compressor 1 when necessary so that an operation stop should not occur due to a pressure drop of low pressure.
  • the controller S controls the fluid-controlled valve 8 of the bypass circuit B to open while continuing the operation of the high-temperature compressor 1 in the high-temperature refrigeration cycle Ra. Further, the controller S switches the four-way valve 11 in the low-temperature refrigeration cycle Rb and also restarts the operation of the low-temperature compressor 10.
  • a hot gas as a refrigerant gas at high temperature and pressure discharged from the high-temperature compressor 1 is guided to the bypass circuit B and then guided into the heat sink 5a of the intermediate heat exchanger 5 via the fluid-controlled valve 8 to give off high heat.
  • a liquid refrigerant present in the water heat exchanger 2 as a condenser and the liquid receiver 3 is depressed and boiled before being gasified to circulate in the opposite direction in the refrigeration cycle.
  • the gasified refrigerant is guided to the bypass circuit B and then guided into the intermediate heat exchanger 5 via the fluid-controlled valve 8. Accordingly, heat is also absorbed from hot water on the side of use to provide a portion of the heat source needed for defrosting operation.
  • the refrigerant circulates in the direction opposite to the direction during hot water supply operation using the intermediate heat exchanger 5 as a heat source and the refrigerant is condensed in each of the aero-thermal exchangers 12 to give off heat of condensation.
  • frost adhering to the aero-thermal exchanger 12 is gradually melted and drops as drain water. The frost is quickly thinned to expose the surface of the aero-thermal exchanger 12.
  • All stored heat is used to defrost the aero-thermal exchanger 12, further promoting a defrosting operation.
  • the controller S detects that high pressure of the high-temperature refrigeration cycle Ra has dropped to a predetermined pressure or less, the controller S executes control to totally close the fluid-controlled valve 8 of the bypass circuit B and also executes control to open the high-temperature expansion device 4 totally or to an appropriate degree of opening.
  • a discharge gas at low temperature in the high-temperature refrigeration cycle Ra can be warmed by heat of hot water guided into the water heat exchanger 2 so that a heat source of the defrosting operation of the aero-thermal exchanger 12 can be ensured.
  • the temperature drop of hot water guided into the water heat exchanger 2 can be limited to less than 1 degree.
  • high-temperature expansion device 4 is adjusted to an appropriate degree of opening, instead of totally opening the high-temperature expansion device 4, high pressure of the high-temperature refrigeration cycle Ra can be slightly increased and thus, the amount of heat by input of the high-temperature compressor 1 can be ensured and also the supply amount of hot gas to the intermediate heat exchanger 5 can be adjusted.
  • the defrosting operation of the aero-thermal exchanger 12 is performed as described above and thus, the need for the four-way valve in the high-temperature refrigeration cycle Ra can be eliminated and also the need for piping parts to be connected to the four-way valve can be eliminated. Therefore, parts costs can be reduced and improvement in workability and also cost reductions can be achieved due to eliminated piping, contributing to miniaturization of devices from reduced installation space thereof.
  • bypass pipe 9 and the fluid-controlled valve 8 constituting the bypass circuit B are needed as a substitute for eliminating the need for the four-way valve in the high-temperature refrigeration cycle Ra, but both ends of the bypass pipe 9 only need to be connected to an intermediate portion of the refrigerant pipe P constituting the high-temperature refrigeration cycle Ra and the fluid-controlled valve 8 can be installed simply as an on-off valve so that the effect on cost can be reduced to a minimum.
  • the rise in low pressure of the high-temperature refrigeration cycle Ra, the rise in discharge temperature accompanying an increase in SH amount, and further the rise in high pressure and the rise in discharge temperature of the low-temperature refrigeration cycle Rb can be obtained by relatively simple control of only throttling the high-temperature expansion device 4 immediately before a defrosting operation being started.
  • the amount of heat needed for defrosting operation can internally be stored in low-pressure piping parts, the high-temperature compressor 1, and high-pressure piping parts in the high-temperature refrigeration cycle Ra and the low-temperature compressor 10 and high-pressure piping parts in the low-temperature refrigeration cycle Rb so that defrosting efficiency can be improved.
  • the operation of the low-temperature compressor 10 in the low-temperature refrigeration cycle Rb is stopped for a predetermined time to balance the pressure on the high-pressure side and the low-pressure side and then the four-way valve 11 is switched and thus, switching noise can be reduced and quiet operation can be achieved.
  • the fluid-controlled valve 8 of the bypass circuit B is controlled to open and the high-temperature expansion device 4 is controlled to close while the operation of the high-temperature compressor 1 being continued. Therefore, hot water as a heat source for defrosting is hardly used so that the temperature drop of hot water guided into the hot water pipe H can be limited. Thus, the heat storage state can be retained while high pressure of the high-temperature refrigeration cycle Ra being maintained, which is helpful in reducing the defrosting time.
  • the fluid-controlled valve 8 of the bypass circuit B is controlled to close and the high-temperature expansion device 4 is controlled to open totally or to an appropriate degree of opening. Therefore, even if input of the high-temperature compressor 1 and the low-temperature compressor 10 is in a minimum state after internal heat storage being used up, a discharge gas of the high-temperature compressor 1 can be warmed by hot water of the hot water pipe H so that the heat source can be ensured, reducing the risk of incomplete defrosting.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP11828854.7A 2010-09-27 2011-09-20 Système d'alimentation en eau chaude Withdrawn EP2623898A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010215911 2010-09-27
PCT/JP2011/071326 WO2012043297A1 (fr) 2010-09-27 2011-09-20 Système d'alimentation en eau chaude

Publications (2)

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EP2623898A1 true EP2623898A1 (fr) 2013-08-07
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EP4257891A4 (fr) * 2020-12-01 2024-05-01 Daikin Industries, Ltd. Système à cycle de réfrigération

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EP4257891A4 (fr) * 2020-12-01 2024-05-01 Daikin Industries, Ltd. Système à cycle de réfrigération

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EP2623898A4 (fr) 2018-01-17
CN102884384A (zh) 2013-01-16
JPWO2012043297A1 (ja) 2014-02-06
WO2012043297A1 (fr) 2012-04-05
KR20130006495A (ko) 2013-01-16

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