WO2012043297A1 - Système d'alimentation en eau chaude - Google Patents

Système d'alimentation en eau chaude Download PDF

Info

Publication number
WO2012043297A1
WO2012043297A1 PCT/JP2011/071326 JP2011071326W WO2012043297A1 WO 2012043297 A1 WO2012043297 A1 WO 2012043297A1 JP 2011071326 W JP2011071326 W JP 2011071326W WO 2012043297 A1 WO2012043297 A1 WO 2012043297A1
Authority
WO
WIPO (PCT)
Prior art keywords
temperature side
refrigeration cycle
high temperature
heat exchanger
low
Prior art date
Application number
PCT/JP2011/071326
Other languages
English (en)
Japanese (ja)
Inventor
貴宏 図司
峻 浅利
Original Assignee
東芝キヤリア株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to EP11828854.7A priority Critical patent/EP2623898A4/fr
Priority to JP2012536353A priority patent/JPWO2012043297A1/ja
Priority to KR1020127028591A priority patent/KR20130006495A/ko
Priority to CN2011800229814A priority patent/CN102884384A/zh
Publication of WO2012043297A1 publication Critical patent/WO2012043297A1/fr

Links

Images

Classifications

    • 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

  • Embodiment of the present invention relates to a hot water supply system that supplies hot water using a two-way refrigeration cycle.
  • the high temperature side refrigeration cycle and the low temperature side refrigeration cycle are connected via an intermediate heat exchanger, and the intermediate heat exchanger exchanges heat between the refrigerant circulating in the high temperature side refrigeration cycle and the refrigerant circulating in the low temperature side refrigeration cycle.
  • a binary refrigeration cycle for obtaining a high compression ratio is frequently used (for example, Japanese Unexamined Patent Publication No. 2000-320914).
  • a water heat exchanger is provided as a condenser constituting the high temperature side refrigeration cycle, and water or hot water is led through a hot water pipe here.
  • the water or hot water is supplied to the use side of the hot water piping destination instead of hot water. Therefore, efficient hot water supply operation is possible even in cold regions.
  • the air heat exchanger that constitutes the low temperature side refrigeration cycle acts as an evaporator during hot water supply operation, so that the air heat exchanger can be frosted especially during operation under low outside air temperature conditions. Is inevitable. If it passes in this state, since the heat exchange efficiency of an air heat exchanger will fall, it is necessary to perform a defrost operation.
  • the four-way switching valve of the high-temperature side refrigeration cycle and the four-way switching valve of the low-temperature side refrigeration cycle are switched to reverse the refrigerant circulation direction. Since the heat source at the time of defrosting is the hot water led to the water heat exchanger of the high temperature side refrigeration cycle, it is possible to maintain the high pressure and the discharge temperature during the defrosting operation. Since the high-temperature gas refrigerant is directly guided to the air heat exchanger of the low-temperature refrigeration cycle, the air heat exchanger is efficiently defrosted.
  • the four-way switching valve is expensive. If possible, the four-way switching valve and piping connected to the four-way switching valve should be deleted to reduce the cost by reducing the parts cost. At the same time, there is a demand to improve the workability of piping work by eliminating the four-way switching valve and the space for connecting piping.
  • This embodiment is based on the above circumstances, and is provided with a dual refrigeration cycle, and performs specific control during the defrosting operation for the evaporator of the low temperature side refrigeration cycle, thereby reducing the component cost and improving the efficiency.
  • a hot water supply system capable of good defrosting operation is provided.
  • the hot water supply system in the present invention includes a low-temperature side compressor, a four-way switching valve, an intermediate heat exchanger, a low-temperature side expansion device, a low-temperature side refrigeration cycle that communicates an evaporator via a refrigerant pipe, and a high-temperature side.
  • a high-temperature side refrigeration cycle configured to communicate a compressor, a water heat exchanger, a high-temperature side expansion device, and an intermediate heat exchanger via a refrigerant pipe, the refrigerant guided to the low-temperature side refrigeration cycle, and the high-temperature side refrigeration cycle
  • the refrigerant led to the refrigerant is led to the binary refrigeration cycle for exchanging heat with the intermediate heat exchanger and the water heat exchanger of the high temperature side refrigeration cycle, and is introduced into the circulating water or hot water and the high temperature side refrigeration cycle.
  • a hot water pipe for supplying heat to the user side one end of which is connected to the refrigerant pipe between the high temperature side compressor and the water heat exchanger of the high temperature side refrigeration cycle, and the other end of the high temperature side refrigeration cycle.
  • High A bypass circuit connected to a refrigerant pipe between the side expansion device and the intermediate heat exchanger and having a fluid control valve in the middle, and fluid control of the bypass circuit during defrosting operation for the evaporator of the low temperature side refrigeration cycle And a control means for controlling to open the valve and close the high temperature side expansion device of the high temperature refrigeration cycle.
  • FIG. 1 is a configuration diagram of a refrigeration cycle of a hot water supply system according to the present embodiment.
  • FIG. 1 is a refrigeration cycle configuration diagram of a hot water supply system, and particularly shows a refrigeration cycle switching state during a defrosting operation.
  • This hot water supply system includes a high temperature side refrigeration cycle Ra, a hot water pipe H, a low temperature side refrigeration cycle Rb, and a control unit (control means) S.
  • the discharge part a of the high temperature side compressor 1, the water heat exchanger 2, the liquid receiver 3, the high temperature side expansion apparatus 4, and the heat absorption part 5a of the intermediate heat exchanger 5 will be described.
  • the gas-liquid separator 6 is sequentially connected via the refrigerant pipe P, and the gas-liquid separator 6 communicates with the suction part b of the high-temperature side compressor 1.
  • the refrigerant compressed and discharged by the high temperature side compressor 1 is as follows:-water heat exchanger 2-liquid receiver 3-high temperature side expansion device 4-intermediate heat exchanger 5 Endothermic part 5a-gas-liquid separator 6-high temperature side compressor 1-. Therefore, the water heat exchanger 2 acts as a condenser, and the heat absorption part 5a of the intermediate heat exchanger 5 acts as an evaporator.
  • the bypass circuit B is provided in such a high temperature side refrigeration cycle Ra.
  • One end of the bypass circuit B is connected to the refrigerant pipe P between the discharge part a of the high temperature side compressor 1 and the water heat exchanger 2, and the other end is the heat absorption of the high temperature side expansion device 4 and the intermediate heat exchanger 5.
  • It consists of a bypass pipe 9 connected to the refrigerant pipe P between the part 5a and having a fluid control valve 8 in the middle.
  • Hot water pipe H One end of the hot water pipe H is connected to a hot water return pipe or a condensate side buffer tank, and the other end is connected to a hot water outlet pipe or an outgoing side buffer tank (both not shown).
  • the middle part of the hot water pipe H is piped to the water heat exchanger 2 constituting the high temperature side refrigeration cycle Ra, and water or hot water led to the hot water pipe H and refrigerant led to the water heat exchanger 2 are connected. Heat exchange is possible.
  • the discharge part c of the low temperature side compressor 10 and the first port d1 of the four-way switching valve 11 are connected via the refrigerant pipe P, and the second port d2 of the four-way switching valve 11 is in the middle.
  • the heat radiating part 5b of the heat exchanger 5 is connected via the refrigerant pipe P.
  • the third port d3 of the four-way switching valve 11 is connected to the two air heat exchangers 12 and 12 here through a refrigerant pipe P branched from the middle part into two.
  • the fourth port d4 of the four-way switching valve 11 is connected to the suction part e of the low temperature side compressor 10 via the gas-liquid separator 13 via the refrigerant pipe P.
  • the heat radiating part 5b of the intermediate heat exchanger 5 is connected to the liquid receiver 14 via the refrigerant pipe P, and the liquid receiver 14 and the two air heat exchangers 12 are branched from the middle part into two. Each is connected via a refrigerant pipe P provided with a low temperature side expansion device 15.
  • the refrigerant compressed and discharged by the low temperature side compressor 10 is as follows:-four-way switching valve 11-heat radiation part 5b of the intermediate heat exchanger 5-low temperature of the receiver 14-2
  • the side expansion device 15-2 is guided in the order of the air heat exchanger 12-four-way switching valve 11-gas-liquid separator 13-low temperature side compressor 10-.
  • the heat radiation part 5b of the intermediate heat exchanger 5 acts as a condenser, and the air heat exchanger 12 acts as an evaporator.
  • the four-way switching valve 11 is switched in the direction shown in the figure, and the refrigerant compressed and discharged by the low-temperature side compressor 10 is: Air heat exchanger 12-2 low temperature side expansion device 15-liquid receiver 14-heat radiation part 5b of intermediate heat exchanger 5-four-way switching valve 11-gas-liquid separator 13-low temperature side compressor 10- It is burned. At this time, the air heat exchanger 12 acts as a condenser, and the heat radiating portion of the intermediate heat exchanger 5 acts as an evaporator.
  • the controller S includes temperature sensors provided at the discharge portions a and c and the suction portions b and e of the high-temperature side compressor 1 and the low-temperature side compressor 10, and pressures provided at the discharge portions a and c and the suction portions b and e. Detected from a sensor, a temperature sensor provided in the water heat exchanger 2, a temperature sensor provided in the heat absorbing part 5a and the heat radiating part 5b of the intermediate heat exchanger 5, a temperature sensor provided in the air heat exchanger 12 (all not shown), etc. Receive a signal.
  • control unit S receives the instruction signal from the remote controller (remote controller), performs calculation, and compares it with the reference value (heating capacity or temperature at the intermediate heat exchanger 5) to be stored with the high-temperature side compressor 1.
  • the operating frequency of the low temperature side compressor 10 is controlled.
  • the superheat amount (hereinafter referred to as “SH amount”) of the heat exchanger is calculated from the difference between the refrigerant temperature of the heat exchanger and the suction side refrigerant temperature of the compressor, and the high temperature side expansion device 4 and the low temperature
  • the throttle amount of the side expansion device 15 is controlled.
  • the fluid control valve 8 of the bypass circuit B is controlled to open and close.
  • the control unit S controls the high temperature side refrigeration cycle Ra and the low temperature side refrigeration cycle Rb to guide and circulate the refrigerant as described above.
  • the refrigerant condenses in the heat radiating part 5b on the low temperature side refrigeration cycle Rb side to release condensation heat, and the refrigerant evaporates while absorbing the heat of condensation in the heat absorbing part 5a on the high temperature side refrigeration cycle Ra side. To do.
  • the temperature difference between the evaporation temperature in the air heat exchanger 12 and the condensation temperature in the water heat exchanger 2 becomes large, and a high compression ratio can be obtained.
  • the water or hot water led to the hot water pipe H absorbs the hot heat of condensation and the temperature rises efficiently.
  • the water or hot water is changed to hot water, and circulates between the water heat exchanger 2 -the buffer tank on the warm water supply side, the buffer tank on the load side, and the water heat exchanger 2.
  • the air heat exchanger 12 in the low temperature side refrigeration cycle Rb performs the evaporation of the refrigerant, so that the condensed water generated here freezes and becomes frost. Adhere as it is. As time elapses, the thickness of the frost increases, and the heat exchange efficiency in the air heat exchanger 12 decreases.
  • Control part S receives the detection signal from the temperature sensor attached to the air heat exchanger 12, and receives the detection signal from other sensors, and judges the necessity for the defrost operation with respect to the air heat exchanger 12.
  • FIG. As a result, the defrosting operation is performed, but the control unit S actually performs the control described below immediately before the start of the defrosting operation.
  • control unit S performs control to throttle the high temperature side expansion device 4 provided in the high temperature side refrigeration cycle Ra at a timing immediately before the start of the defrosting operation. Therefore, in the high temperature side refrigeration cycle Ra, the flow rate of the refrigerant guided from the high temperature side expansion device 4 to the heat absorption part 5a of the intermediate heat exchanger 5 decreases.
  • the amount of heat absorbed by the heat absorption part 5a of the intermediate heat exchanger 5 decreases, the temperature of the heat absorption part 5a and the heat dissipation part 5b rises, and the temperature of the intermediate heat exchanger 5 as a whole also rises. At this time, it is not necessary to change the operating frequencies of the high temperature side compressor 1 in the high temperature side refrigeration cycle Ra and the low temperature side compressor 10 in the low temperature side refrigeration cycle Rb.
  • the suction temperature and suction pressure of the high-temperature compressor 1 communicating with the heat-absorbing part 5a of the intermediate heat exchanger 5 via the refrigerant pipe P also rise, but the refrigerant circulation rate decreases in the high-temperature refrigeration cycle Ra, so that the discharge There is almost no increase in pressure, and the compression ratio of the high temperature side compressor 1 decreases.
  • the controller S controls the expansion of the high temperature side expansion device 4 of the high temperature side refrigeration cycle Ra at the timing immediately before the start of the defrosting operation for the air heat exchanger 12. Therefore, without changing the operating frequency of the high temperature side compressor 1 and the low temperature side compressor 10, the evaporation temperature rise of the heat absorption part 5a and the condensation temperature rise of the heat radiating part 5b of the intermediate heat exchanger 5 can be increased in a short time. The discharge temperature rise of the compressor 1 and the low temperature side compressor 10 can be obtained.
  • the temperature of the low pressure side piping components from the high temperature side expansion device 4 via the intermediate heat exchanger 5 to the high temperature side compressor 1 rises, and the compressor body of the high temperature side compressor 1 and the high temperature side
  • the high-pressure side piping parts from the side compressor 1 to the water heat exchanger 2 also rise in temperature, and heat storage can be achieved.
  • the controller S controls the actual start of the defrosting operation for the air heat exchanger 12.
  • the fluid control valve 8 of the bypass circuit B is opened, and the four-way switching valve 11 of the low-temperature side refrigeration cycle Rb is switched to supply the refrigerant in the direction opposite to the refrigerant circulation direction in the low-temperature side refrigeration cycle Rb. Circulate.
  • control unit S temporarily stops the operation of the low temperature side compressor 10 (several tens of seconds to several minutes) and performs necessary control such as opening the pressure equalizing pipe so that the high pressure side in the low temperature side refrigeration cycle Rb. Balance the pressure on the low pressure side in a short time.
  • the four-way switching valve 11 the refrigerant flow inside the switching valve is lowered, the collision is calmed down, and switching noise can be suppressed.
  • the control unit S fully closes the high temperature side expansion device 4 while continuing the operation of the high temperature side compressor 1 in the high temperature side refrigeration cycle Ra. Therefore, the high pressure of the high temperature side refrigeration cycle Ra is maintained, the refrigerant recovered from the heat absorption part 5a of the intermediate heat exchanger 5 and discharged from the high temperature side compressor 1 is the water heat exchanger 2 and the receiver that are condensers. 3 is stored as a high-temperature liquid refrigerant. Further, since the refrigerant is not supplied to the intermediate heat exchanger 5, the amount of heat absorbed from the heat absorbing portion 5a can be suppressed, and the heat storage effect is maintained.
  • the pump-down (refrigerant recovery) operation is performed in the high-temperature side refrigeration cycle Ra, the operation is performed by reducing the operation frequency of the high-temperature side compressor 1 as necessary so that the operation is not stopped due to a decrease in the low pressure. It is desirable to extend the duration.
  • the control unit S controls the opening of the fluid control valve 8 of the bypass circuit B while continuing the operation of the high temperature side compressor 1 of the high temperature side refrigeration cycle Ra. Further, the four-way switching valve 11 of the low temperature side refrigeration cycle Rb is switched, and the operation of the low temperature side compressor 10 is restarted. At this time, in the low temperature side refrigeration cycle Rb, since the pressures on the high pressure side and the low pressure side are balanced, the switching sound of the four-way switching valve 11 hardly occurs.
  • Hot gas which is a high-temperature and high-pressure refrigerant gas discharged from the high-temperature side compressor 1, is led to the bypass circuit B, and is led to the heat absorption part 5a of the intermediate heat exchanger 5 via the fluid control valve 8 to release high heat. Further, in the process in which the high pressure of the high temperature side refrigeration cycle Ra is decreasing, the liquid heat refrigerant 2 in the hydrothermal exchanger 2 as a condenser and the liquid receiver 3 is boiled under reduced pressure, gasified, and flows backward in the refrigeration cycle.
  • the gasified refrigerant is led to the bypass circuit B and led to the intermediate heat exchanger 5 via the fluid control valve 8.
  • heat is absorbed from the hot water on the use side, and a part of the heat source necessary for the defrosting operation can be covered.
  • the refrigerant circulates in the direction opposite to that during hot water supply operation, and the refrigerant is condensed in each air heat exchanger 12 to release the condensation heat. Therefore, the frost adhering to the air heat exchanger 12 is gradually melted and dripped as drain water. The thickness of the frost decreases immediately, and the background of the air heat exchanger 12 is exposed.
  • the low-pressure side piping component extending from the high-temperature side expansion device 4 of the high-temperature side refrigeration cycle Ra to the high-temperature side compressor 1 via the intermediate heat exchanger 5.
  • the heat stored in the high-pressure side piping components extending from to the low-temperature side expansion device 15 via the intermediate heat exchanger 5 is released at this time. Since all of these heat storages are spent for defrosting the air heat exchanger 12, the defrosting action is further promoted.
  • control unit S controls the fluid control valve 8 of the bypass circuit B to be fully closed while detecting that the high pressure of the high temperature side refrigeration cycle Ra has dropped below a predetermined pressure, and the high temperature side expansion device 4 Control to fully open or optimal opening.
  • the low temperature discharge gas of the high temperature side refrigeration cycle Ra can be heated by the heat of the hot water led to the water heat exchanger 2, and a heat source for the defrosting operation for the air heat exchanger 12 is secured.
  • the temperature drop of the hot water led to the water heat exchanger 2 at this time is less than 1 ° C.
  • the high pressure of the high temperature side refrigeration cycle Ra can be slightly increased, so that the heat quantity is secured by the input of the high temperature side compressor 1 and intermediate heat exchange is performed. It is possible to adjust the amount of hot gas supplied to the vessel 5.
  • the four-way switching valve in the high-temperature side refrigeration cycle Ra is not required, and the piping parts to be connected to the four-way switching valve are not required, thereby reducing component costs.
  • bypass pipe 9 and the fluid control valve 8 constituting the bypass circuit B are required, but both ends of the bypass pipe 9 constitute the high temperature side refrigeration cycle Ra. Since the fluid control valve 8 can be a simple on-off valve, it is possible to suppress the influence on the cost to a minimum.
  • the discharge temperature rises as the low-pressure rise of the high-temperature side refrigeration cycle Ra and the SH amount increase by the relatively simple control that only throttles the high-temperature side expansion device 4.
  • Rb high pressure rise and discharge temperature rise can be obtained.
  • the low pressure side piping component, the high temperature side compressor 1 and the high pressure side piping component in the high temperature side refrigeration cycle Ra, and the low pressure side compressor 10 and the high pressure side piping component in the low temperature side refrigeration cycle Rb are required during the defrosting operation.
  • the amount of heat that becomes can be stored internally, and the defrosting efficiency can be improved.
  • the operation of the low temperature side compressor 10 in the low temperature side 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 switching valve 11 Since the switching is made, the switching noise can be reduced and the silent operation can be performed.
  • the fluid control valve 8 of the bypass circuit B is opened while the operation of the high temperature side compressor 1 is continued, and the high temperature side expansion device 4 is closed. Therefore, almost no hot water is used as a heat source at the time of defrosting, and the temperature drop of the hot water led to the hot water pipe H can be suppressed.
  • the high pressure of the high temperature side refrigeration cycle Ra can be maintained to maintain the heat storage state, which helps shorten the defrosting time.
  • the fluid control valve 8 of the bypass circuit B is closed, and the high temperature side expansion device 4 is fully opened or controlled to an optimal opening. Therefore, even if the internal heat storage is exhausted and the inputs of the high temperature side compressor 1 and the low temperature side compressor 10 become extremely small, the discharge gas of the high temperature side compressor 1 can be warmed by the hot water of the hot water pipe H, and the heat source Therefore, the risk that defrosting is not completed can be reduced.

Landscapes

  • 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)

Abstract

L'invention porte sur un cycle de réfrigération binaire qui est formé à partir d'un cycle de réfrigération côté basse température (Rb) nécessitant une valve de commutation à quatre voies (11) et un cycle de réfrigération côté haute température (Ra) ne nécessitant pas de valve de commutation à quatre voies (11), et une chaleur est échangée au moyen d'un échangeur de chaleur intermédiaire (5) disposé dans chacun des cycles de réfrigération. Un tuyau d'eau chaude (H) est posé dans un échangeur de chaleur à eau (2) du cycle de réfrigération côté haute température (Ra) et de l'eau ou de l'eau chaude est fournie pour une utilisation en tant qu'eau chaude ayant une température élevée. Une extrémité d'un circuit de dérivation (B) est reliée à un tuyau de réfrigérant (P) entre l'échangeur de chaleur à eau et un compresseur côté haute température (1) du cycle de réfrigération côté haute température (Ra), l'autre extrémité étant reliée à un tuyau de réfrigérant entre un dispositif d'expansion côté haute température (4) et l'échangeur de chaleur intermédiaire, et une valve de commande de fluide (8) étant disposée à mi-chemin entre les deux extrémités. Une unité de commande (S) réalise une commande, de sorte que la valve de commande de fluide (8) soit ouverte et que le dispositif d'expansion côté haute température soit fermé pendant une opération de dégivrage pour un échangeur de chaleur à air (12) du cycle de réfrigération côté basse température (Rb), et atteint ainsi une commande spécifique pendant une opération de dégivrage pour un évaporateur du cycle de réfrigération côté basse température (Rb) et rend possible de réduire le nombre de composants et d'effectuer des opérations de dégivrage efficaces.
PCT/JP2011/071326 2010-09-27 2011-09-20 Système d'alimentation en eau chaude WO2012043297A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP11828854.7A EP2623898A4 (fr) 2010-09-27 2011-09-20 Système d'alimentation en eau chaude
JP2012536353A JPWO2012043297A1 (ja) 2010-09-27 2011-09-20 給湯システム
KR1020127028591A KR20130006495A (ko) 2010-09-27 2011-09-20 급탕 시스템
CN2011800229814A CN102884384A (zh) 2010-09-27 2011-09-20 供热水系统

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-215911 2010-09-27
JP2010215911 2010-09-27

Publications (1)

Publication Number Publication Date
WO2012043297A1 true WO2012043297A1 (fr) 2012-04-05

Family

ID=45892761

Family Applications (1)

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

Country Status (5)

Country Link
EP (1) EP2623898A4 (fr)
JP (1) JPWO2012043297A1 (fr)
KR (1) KR20130006495A (fr)
CN (1) CN102884384A (fr)
WO (1) WO2012043297A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014083932A1 (fr) * 2012-11-30 2014-06-05 ダイキン工業株式会社 Système de chauffage d'eau
JP2014105891A (ja) * 2012-11-26 2014-06-09 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水生成装置
EP2990737A4 (fr) * 2013-04-26 2016-12-07 Toshiba Carrier Corp Dispositif d'alimentation en eau chaude
CN106288476A (zh) * 2016-09-23 2017-01-04 苏州热火能源科技有限公司 一种双温升的复叠式热泵
WO2022118842A1 (fr) * 2020-12-01 2022-06-09 ダイキン工業株式会社 Système à cycle frigorifique
WO2023190233A1 (fr) * 2022-03-30 2023-10-05 株式会社富士通ゼネラル Dispositif pompe à chaleur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114341569B (zh) * 2019-09-30 2023-04-28 大金工业株式会社 热源机组及制冷装置
CN116601443A (zh) * 2020-12-01 2023-08-15 大金工业株式会社 冷冻循环系统

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61175430A (ja) * 1985-01-31 1986-08-07 Tohoku Electric Power Co Inc 冷凍サイクル
JPH0424478A (ja) * 1990-05-17 1992-01-28 Daikin Ind Ltd 冷凍装置
JPH04288463A (ja) * 1991-02-25 1992-10-13 Mitsubishi Electric Corp 空気調和機
JPH1096573A (ja) * 1996-09-24 1998-04-14 Daikin Ind Ltd 空気調和機
JPH1130461A (ja) * 1997-03-12 1999-02-02 Matsushita Electric Ind Co Ltd 冷凍サイクル制御装置
JP2000320914A (ja) 1999-05-14 2000-11-24 Daikin Ind Ltd 冷凍装置
JP2002243276A (ja) * 2001-02-20 2002-08-28 Toshiba Kyaria Kk ヒートポンプ給湯器
JP2003074998A (ja) * 2001-09-04 2003-03-12 Sanyo Electric Co Ltd 冷凍サイクル装置
JP2010196950A (ja) * 2009-02-24 2010-09-09 Daikin Ind Ltd ヒートポンプシステム

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60164157A (ja) * 1984-02-07 1985-08-27 Matsushita Electric Ind Co Ltd ヒ−トポンプ給湯機
JPS61101771A (ja) * 1984-10-23 1986-05-20 三菱電機株式会社 ヒ−トポンプ式冷暖房給湯機
JPS63286676A (ja) * 1987-05-18 1988-11-24 三菱電機株式会社 空気調和装置
JPH01144770U (fr) * 1988-03-30 1989-10-04
JPH06123527A (ja) * 1992-10-12 1994-05-06 Hitachi Ltd 冷凍・冷蔵ユニットの冷凍サイクル
JPH09119754A (ja) * 1995-10-27 1997-05-06 Hitachi Ltd 空気調和機
JP3909311B2 (ja) * 2003-06-24 2007-04-25 日立アプライアンス株式会社 ヒートポンプ給湯機
JP2009109069A (ja) * 2007-10-30 2009-05-21 Panasonic Corp ヒートポンプ給湯機
JP5551882B2 (ja) * 2009-02-24 2014-07-16 ダイキン工業株式会社 ヒートポンプシステム
JP5711448B2 (ja) * 2009-02-24 2015-04-30 ダイキン工業株式会社 ヒートポンプシステム

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61175430A (ja) * 1985-01-31 1986-08-07 Tohoku Electric Power Co Inc 冷凍サイクル
JPH0424478A (ja) * 1990-05-17 1992-01-28 Daikin Ind Ltd 冷凍装置
JPH04288463A (ja) * 1991-02-25 1992-10-13 Mitsubishi Electric Corp 空気調和機
JPH1096573A (ja) * 1996-09-24 1998-04-14 Daikin Ind Ltd 空気調和機
JPH1130461A (ja) * 1997-03-12 1999-02-02 Matsushita Electric Ind Co Ltd 冷凍サイクル制御装置
JP2000320914A (ja) 1999-05-14 2000-11-24 Daikin Ind Ltd 冷凍装置
JP2002243276A (ja) * 2001-02-20 2002-08-28 Toshiba Kyaria Kk ヒートポンプ給湯器
JP2003074998A (ja) * 2001-09-04 2003-03-12 Sanyo Electric Co Ltd 冷凍サイクル装置
JP2010196950A (ja) * 2009-02-24 2010-09-09 Daikin Ind Ltd ヒートポンプシステム

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2623898A4

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014105891A (ja) * 2012-11-26 2014-06-09 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水生成装置
WO2014083932A1 (fr) * 2012-11-30 2014-06-05 ダイキン工業株式会社 Système de chauffage d'eau
JP2014109405A (ja) * 2012-11-30 2014-06-12 Daikin Ind Ltd 水加熱システム
EP2990737A4 (fr) * 2013-04-26 2016-12-07 Toshiba Carrier Corp Dispositif d'alimentation en eau chaude
CN106288476A (zh) * 2016-09-23 2017-01-04 苏州热火能源科技有限公司 一种双温升的复叠式热泵
WO2022118842A1 (fr) * 2020-12-01 2022-06-09 ダイキン工業株式会社 Système à cycle frigorifique
JP7436933B2 (ja) 2020-12-01 2024-02-22 ダイキン工業株式会社 冷凍サイクルシステム
WO2023190233A1 (fr) * 2022-03-30 2023-10-05 株式会社富士通ゼネラル Dispositif pompe à chaleur
JP2023147886A (ja) * 2022-03-30 2023-10-13 株式会社富士通ゼネラル ヒートポンプ装置
JP7380739B2 (ja) 2022-03-30 2023-11-15 株式会社富士通ゼネラル ヒートポンプ装置

Also Published As

Publication number Publication date
EP2623898A4 (fr) 2018-01-17
CN102884384A (zh) 2013-01-16
EP2623898A1 (fr) 2013-08-07
JPWO2012043297A1 (ja) 2014-02-06
KR20130006495A (ko) 2013-01-16

Similar Documents

Publication Publication Date Title
WO2012043297A1 (fr) Système d'alimentation en eau chaude
JP5659292B2 (ja) 二元冷凍サイクル装置
JP5595245B2 (ja) 冷凍装置
JP4974714B2 (ja) 給湯器
WO2009098751A1 (fr) Système complexe de climatisation et de chauffe-eau
US8950202B2 (en) Heat pump system
WO2010113372A1 (fr) Système combiné composé d'un dispositif de climatisation et d'un dispositif d'alimentation en eau chaude
US20110289950A1 (en) Hot water supply apparatus associated with heat pump
JP5094942B2 (ja) ヒートポンプ装置
WO2014024837A1 (fr) Équipement frigorifique en cascade
JP2008185229A (ja) 冷凍装置
CN102032699A (zh) 冷冻循环装置以及水暖装置
JP2008096033A (ja) 冷凍装置
WO2017037771A1 (fr) Dispositif à cycle de réfrigération
JP6057871B2 (ja) ヒートポンプシステム、及び、ヒートポンプ式給湯器
JP5904628B2 (ja) デフロスト運転用の冷媒管を備えた冷凍サイクル
KR20140123384A (ko) 공기열 이원 사이클 히트펌프 냉난방 장치
US20210207834A1 (en) Air-conditioning system
JP2017026171A (ja) 空気調和装置
JP2014081180A (ja) ヒートポンプ装置
JP4898025B2 (ja) マルチ型ガスヒートポンプ式空気調和装置
JP5150300B2 (ja) ヒートポンプ式給湯装置
JP3993540B2 (ja) 冷凍装置
JP2017161159A (ja) 空気調和機の室外ユニット
GB2458901A (en) Heat pump system with first and second compressors

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201180022981.4

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11828854

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2012536353

Country of ref document: JP

ENP Entry into the national phase

Ref document number: 20127028591

Country of ref document: KR

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2011828854

Country of ref document: EP