WO2012043297A1 - 給湯システム - Google Patents
給湯システム Download PDFInfo
- 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
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 96
- 238000005057 refrigeration Methods 0.000 claims abstract description 109
- 239000003507 refrigerant Substances 0.000 claims abstract description 59
- 238000010257 thawing Methods 0.000 claims abstract description 42
- 239000012530 fluid Substances 0.000 claims abstract description 18
- 230000009977 dual effect Effects 0.000 claims description 2
- 239000007788 liquid Substances 0.000 description 14
- 238000010521 absorption reaction Methods 0.000 description 9
- 238000005338 heat storage Methods 0.000 description 9
- 230000007423 decrease Effects 0.000 description 8
- 230000005494 condensation Effects 0.000 description 6
- 238000009833 condensation Methods 0.000 description 6
- 238000001704 evaporation Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 230000005855 radiation Effects 0.000 description 3
- 238000001514 detection method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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.
Abstract
Description
温水配管Hの中途部は、上記高温側冷凍サイクルRaを構成する水熱交換器2に配管されていて、温水配管Hに導かれる水もしくは温水と、水熱交換器2に導かれる冷媒とが熱交換できる。
このときは、空気熱交換器12が凝縮器として作用し、中間熱交換器5の放熱部が蒸発器として作用する。
さらに、熱交換器の冷媒温度と圧縮機の吸込み側冷媒温度との差から、熱交換器のスーパーヒート量(以下、「SH量」と呼ぶ)を算出して、高温側膨張装置4と低温側膨張装置15の絞り量を制御する。そして、バイパス回路Bの流体制御弁8を開閉制御する。
上記中間熱交換器5では、低温側冷凍サイクルRb側の放熱部5bで冷媒が凝縮して凝縮熱を放出し、高温側冷凍サイクルRa側の吸熱部5aで冷媒が凝縮熱を吸熱しながら蒸発する。
水熱交換器2において水もしくは温水は高温化した温水と変り、 水熱交換器2-温水往水側のバッファタンク-負荷側復水側バッファタンク-水熱交換器2 と循環する。
また、中間熱交換器5へ冷媒が供給されなくなることにより、吸熱部5aからの吸熱量を抑制することができ、蓄熱効果が維持されることとなる。
このとき、低温側冷凍サイクルRbにおいては、高圧側と低圧側の圧力がバランスしているので、四方切換え弁11の切換え音はほとんど発生しない。
これらの蓄熱は全て、空気熱交換器12に対する除霜のために費やされるので、さらに除霜作用が促進される。
これにより、高温側冷凍サイクルRaの低温の吐出ガスを水熱交換器2に導かれる温水の熱で暖めることができ、空気熱交換器12に対する除霜運転の熱源を確保する。このときの水熱交換器2に導かれる温水の温度低下は1℃未満で済む。
このようにして、空気熱交換器12に対する除霜運転を行うので、高温側冷凍サイクルRaでの四方切換え弁を不要とするとともに、四方切換え弁に接続すべき配管部品を不要として、部品費低減と、配管手間不要による作業性の向上およびコストの削減化を得るとともに、これらの設置スペースの低減から装置の小型化に寄与する。
結果として、高温側冷凍サイクルRaにおける低圧側配管部品、高温側圧縮機1および高圧側配管部品と、低温側冷凍サイクルRbにおける低圧側圧縮機10および高圧側配管部品に、除霜運転時に必要となる熱量を内部蓄熱でき、除霜効率の向上化を図れる。
Claims (4)
- 低温側圧縮機、四方切換え弁、中間熱交換器、低温側膨張装置、蒸発器を冷媒配管を介して連通する低温側冷凍サイクルと、高温側圧縮機、水熱交換器、高温側膨張装置、中間熱交換器を冷媒配管を介して連通する高温側冷凍サイクルとから構成され、上記低温側冷凍サイクルに導かれる冷媒と、上記高温側冷凍サイクルに導かれる冷媒とを、上記中間熱交換器で熱交換させる2元冷凍サイクルと、
上記高温側冷凍サイクルの水熱交換器に配管され、流通する水または温水と高温側冷凍サイクルに導かれる冷媒とを熱交換させて利用側へ供給する温水配管と、
一端が上記高温側冷凍サイクルの高温側圧縮機と水熱交換器との間の冷媒配管に接続され、他端が高温側冷凍サイクルの高温側膨張装置と中間熱交換器との間の冷媒配管に接続され、中途部に流体制御弁を有するバイパス回路と、
上記低温側冷凍サイクルの蒸発器に対する除霜運転時に、上記バイパス回路の流体制御弁を開放し、上記高温冷凍サイクルの高温側膨張装置を閉成するよう制御する制御手段と、
を具備することを特徴とする給湯システム。 - 上記制御手段は、
給湯運転時に、上記低温側冷凍サイクルにおいて、低温側圧縮機-四方切換え弁-中間熱交換器-低温側膨張装置-蒸発器-低温側圧縮機-の順に冷媒を循環制御するとともに、上記高温側冷凍サイクルにおいて、高温側圧縮機-水熱交換器-高温側膨張装置-中間熱交換器の順に冷媒を循環制御し、
上記蒸発器に対する除霜運転の開始前に、高温側冷凍サイクルの高温側膨張装置を絞って冷媒循環量を低下させて運転を行う制御をなし、
上記蒸発器に対する除霜運転時は、上記低温側冷凍サイクルの四方切換え弁を切換えて、低温側圧縮機-四方切換え弁-蒸発器-低温側膨張装置-中間熱交換器-低温側圧縮機- の順に冷媒を循環制御することを特徴とする請求項1記載の給湯システム。 - 上記制御手段は、
上記蒸発器に対する除霜運転の開始にあたって低温側冷凍サイクルの四方切換え弁を切換える際に、高温側冷凍サイクルの高温側圧縮機の運転を継続したまま高温側膨張装置を全閉に制御し、かつ低温側冷凍サイクルの低温側圧縮機の運転を一旦停止する制御をなす
ことを特徴とする請求項2記載の給湯システム。 - 上記制御手段は、
上記蒸発器に対する除霜運転中に、高温側冷凍サイクルの高圧が所定圧力以下になったときに、上記バイパス回路の流体制御弁を閉成するとともに、高温側冷凍サイクルの高温側膨張装置を開くように制御する
ことを特徴とする請求項2記載の給湯システム。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020127028591A KR20130006495A (ko) | 2010-09-27 | 2011-09-20 | 급탕 시스템 |
EP11828854.7A EP2623898A4 (en) | 2010-09-27 | 2011-09-20 | Hot water supply system |
JP2012536353A JPWO2012043297A1 (ja) | 2010-09-27 | 2011-09-20 | 給湯システム |
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 |
---|---|---|---|
JP2010215911 | 2010-09-27 | ||
JP2010-215911 | 2010-09-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012043297A1 true WO2012043297A1 (ja) | 2012-04-05 |
Family
ID=45892761
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/071326 WO2012043297A1 (ja) | 2010-09-27 | 2011-09-20 | 給湯システム |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2623898A4 (ja) |
JP (1) | JPWO2012043297A1 (ja) |
KR (1) | KR20130006495A (ja) |
CN (1) | CN102884384A (ja) |
WO (1) | WO2012043297A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014083932A1 (ja) * | 2012-11-30 | 2014-06-05 | ダイキン工業株式会社 | 水加熱システム |
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 (en) * | 2013-04-26 | 2016-12-07 | Toshiba Carrier Corp | HOT WATER SUPPLY DEVICE |
WO2022118842A1 (ja) * | 2020-12-01 | 2022-06-09 | ダイキン工業株式会社 | 冷凍サイクルシステム |
WO2023190233A1 (ja) * | 2022-03-30 | 2023-10-05 | 株式会社富士通ゼネラル | ヒートポンプ装置 |
Families Citing this family (2)
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 |
WO2022118841A1 (ja) * | 2020-12-01 | 2022-06-09 | ダイキン工業株式会社 | 冷凍サイクルシステム |
Citations (9)
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)
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 (ja) * | 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 |
-
2011
- 2011-09-20 WO PCT/JP2011/071326 patent/WO2012043297A1/ja active Application Filing
- 2011-09-20 CN CN2011800229814A patent/CN102884384A/zh active Pending
- 2011-09-20 EP EP11828854.7A patent/EP2623898A4/en not_active Withdrawn
- 2011-09-20 JP JP2012536353A patent/JPWO2012043297A1/ja active Pending
- 2011-09-20 KR KR1020127028591A patent/KR20130006495A/ko not_active Application Discontinuation
Patent Citations (9)
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)
Title |
---|
See also references of EP2623898A4 |
Cited By (9)
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 (ja) * | 2012-11-30 | 2014-06-05 | ダイキン工業株式会社 | 水加熱システム |
JP2014109405A (ja) * | 2012-11-30 | 2014-06-12 | Daikin Ind Ltd | 水加熱システム |
EP2990737A4 (en) * | 2013-04-26 | 2016-12-07 | Toshiba Carrier Corp | HOT WATER SUPPLY DEVICE |
WO2022118842A1 (ja) * | 2020-12-01 | 2022-06-09 | ダイキン工業株式会社 | 冷凍サイクルシステム |
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 (ja) * | 2022-03-30 | 2023-10-05 | 株式会社富士通ゼネラル | ヒートポンプ装置 |
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 |
---|---|
JPWO2012043297A1 (ja) | 2014-02-06 |
EP2623898A4 (en) | 2018-01-17 |
KR20130006495A (ko) | 2013-01-16 |
CN102884384A (zh) | 2013-01-16 |
EP2623898A1 (en) | 2013-08-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5659292B2 (ja) | 二元冷凍サイクル装置 | |
WO2012043297A1 (ja) | 給湯システム | |
JP4974714B2 (ja) | 給湯器 | |
WO2009098751A1 (ja) | 空調給湯複合システム | |
US8950202B2 (en) | Heat pump system | |
WO2010113372A1 (ja) | 空調給湯複合システム | |
US20110289950A1 (en) | Hot water supply apparatus associated with heat pump | |
JP5094942B2 (ja) | ヒートポンプ装置 | |
JPWO2011092802A1 (ja) | ヒートポンプ装置及び冷媒バイパス方法 | |
WO2014024837A1 (ja) | 二元冷凍装置 | |
JP2012112617A (ja) | 冷凍装置 | |
US20220011014A1 (en) | Air conditioning system | |
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 | |
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 |
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 |