EP1967801B1 - Système de fourniture d'eau chaude - Google Patents

Système de fourniture d'eau chaude Download PDF

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Publication number
EP1967801B1
EP1967801B1 EP07254439.8A EP07254439A EP1967801B1 EP 1967801 B1 EP1967801 B1 EP 1967801B1 EP 07254439 A EP07254439 A EP 07254439A EP 1967801 B1 EP1967801 B1 EP 1967801B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
bypath
compressor
water
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EP07254439.8A
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German (de)
English (en)
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EP1967801A3 (fr
EP1967801A2 (fr
Inventor
Kazuki c/o Mitsubishi Electric Corporation Okada
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP1967801A2 publication Critical patent/EP1967801A2/fr
Publication of EP1967801A3 publication Critical patent/EP1967801A3/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the present invention relates to a heat-pump hot water system of reverse cycle defrosting type.
  • An example of conventional heat-pump hot water systems of non reverse cycle defrosting type which employs a defrosting system in which a defrosting bypass valve is opened so that a high-temperature high-pressure gas refrigerant discharged from a compressor is allowed to bypass a water heat exchanger that exchanges heat between the water and the refrigerant, and introduced directly into an air heat exchanger that exchanges heat between air and the refrigerant through a defrosting bypath, and the air heat exchanger is heated by the heat of condensation of the refrigerant that is condensed into liquid so that the frost is melted by the heat (refer to Japanese Unexamined Patent Application Publication No. 2002-243276 (p. 9, Fig. 1 )).
  • bypass-type conventional heat-pump hot water system of non reverse cycle defrosting type has the problem of the possibility of decreasing the reliability of the compressor due to liquid reverse operation because the condensed fluid refrigerant is introduced into the inlet of the compressor without being converted to a gas refrigerant by the air heat exchanger serving as an evaporator.
  • US 2008/0092568 A1 discloses a hot-water system supply apparatus having the features in the pre-characterising portion of claim 1.
  • a first object of the invention is to provide a hot water system in which the negative performance during defrosting operation is reduced.
  • a second object of the invention is to provide a hot water system in which a proper amount of circulation is ensured by controlling the condition of the refrigerant at the inlet of the compressor during defrosting operation so that the defrosting operation can be completed in a short time.
  • a third object of the invention is to provide a hot water system in which an overheated refrigerant is prevented from flowing into the compressor by controlling the refrigerant at the inlet of the compressor during defrosting operation to prevent the compressor from being heated abnormally, thereby improving the reliability.
  • a fourth object of the invention is to provide a hot water system in which the backflow of liquid to the compressor is prevented by controlling the refrigerant at the inlet of the compressor during defrosting operation to prevent damages on the compressor, thereby improving the reliability.
  • a hot water system includes: a compressor; a four-way valve for switching the direction of the refrigerating cycle during defrosting operation; a water heat exchanger for exchanging heat between water and a refrigerant; a first expansion valve for controlling the flow rate of the refrigerant to reduce the pressure; and an air heat exchanger for exchanging heat between air and the refrigerant, which are connected in that order by a pipeline to form a refrigerating cycle for circulating the refrigerant.
  • the hot water system further includes a bypath for redirecting the refrigerant from a portion of the pipeline in upstream of the first expansion valve to the inlet of the compressor during defrosting operation.
  • the hot water system is characterised by a solenoid valve disposed in the bypath, for switching; a receiver disposed between the first expansion valve and the air heat exchanger; and a second expansion valve disposed between the receiver and the air heat exchanger, wherein the bypath is connected to a portion of the pipeline between the first expansion valve which is downstream of the receiver during defrosting operation and the receiver, wherein there is a difference in internal volume between the water heat exchanger and the air heat exchanger and wherein when the solenoid valve is opened to redirect part of the refrigerant passing through the water heat exchanger acting as an evaporator into the bypath during defrosting operation, the amount of the refrigerant passing through the bypath is controlled by changing the degree of opening of the first expansion valve.
  • the hot water system according to the first aspect of the invention has a bypath for redirecting the refrigerant from a portion of the pipeline in upstream of the first expansion valve to the inlet of the compressor during defrosting operation and a solenoid valve disposed in the bypath, for switching.
  • the solenoid valve is opened to redirect part of the refrigerant passing through the water heat exchanger acting as an evaporator into the bypath during defrosting operation. Therefore, the amount of the refrigerant to the water heat exchanger is reduced. This offers the advantage of reducing the amount of heat exchange to decrease the negative performance during defrosting operation.
  • the amount of the refrigerant to the bypath is controlled by changing the degree of opening of the first expansion valve. This allows the refrigerant at the inlet of the compressor to be controlled, thus offering the advantage of ensuring proper amount of circulation to terminate the defrosting operation in a short time.
  • the proper control of the state of the refrigerant to be sucked in the compressor offers the advantage of.preventing abnormal overheating of the compressor by preventing the inflow of an overheated refrigerant and preventing damages to the compressor due to the backflow of liquid, thus improving the reliability of the compressor.
  • Fig. 1 is a refrigerant circuit diagram of a hot water system.
  • the heat-pump hot water system includes a compressor 1, a four-way valve 2 for switching the refrigerant circuit during defrosting operation, a water heat exchanger 3 that exchanges heat between water and a refrigerant, an electronic expansion valve 4 that controls the flow rate of the refrigerant to decrease the pressure, an air heat exchanger 5 that exchanges heat between air and the refrigerant, and a pipeline 7 that connects the foregoing components.
  • One end of a bypath 8 is connected to a portion of the pipe 7 which is upstream of the electronic expansion valve 4 during defrosting operation, and the other end of the bypath 8 is connected to a portion of a pipe 7 adjacent to the inlet of the compressor 1.
  • the bypath 8 has therein a solenoid on-off valve 9.
  • the solenoid valve 9 When the solenoid valve 9 is opened, the refrigerant can be passed through the bypath 8, and when the solenoid valve 9 is closed, the refrigerant can be stopped.
  • the refrigerant flows from the portion of the pipe 7 in upstream of the high-pressure electronic expansion valve 4 to the inlet of the compressor 1 at a low pressure.
  • Fig. 1 shows the flow of the refrigerant in the refrigerating cycle when the hot water system is operated as a water heater by solid lines.
  • the refrigerant that has become high-pressure high-temperature gas in the compressor 1 is discharged from the outlet of the compressor 1 to the four-way valve 2.
  • the four-way valve 2 is a valve for switching the circuit of the refrigerant. When the hot water system is operated as a water heater, the four-way valve 2 is fixed so as to feed the refrigerant discharged from the compressor 1 to the water heat exchanger 3.
  • the refrigerant fed to the water heat exchanger 3 exchanges heat with the water in the water heat exchanger 3.
  • the high-pressure high-temperature gas refrigerant gives heat to the water, and is condensed into a high-pressure normal-temperature liquid refrigerant.
  • the water flowing into the water heat exchanger 3 receives the heat from the refrigerant to be increased in temperature and is discharged.
  • the water heat exchanger 3 thus acts as a condenser of the refrigerating cycle.
  • the electronic expansion valve 4 controls the refrigerant condensed by the water heat exchanger 3 acting as a condenser according to the degree of subcooling.
  • the degree of opening of the electronic expansion valve 4 When the degree of subcooling is low, the degree of opening of the electronic expansion valve 4 is decreased so that the liquid of the refrigerant condensed by the water heat exchanger 3 is increased to thereby increase the degree of subcooling. In contrast, when the degree of subcooling is high, the degree of opening of the electronic expansion valve 4 is increased so that the liquid of the refrigerant condensed by the water heat exchanger 3 is decreased to thereby decrease the degree of subcooling.
  • the refrigerant discharged from the water heat exchanger 3 is reduced in pressure by the electronic expansion valve 4 that controls the flow rate of the refrigerant to decrease the pressure, and becomes a low-pressure low-temperature liquid refrigerant.
  • the refrigerant flows from the electronic expansion valve 4 to the air heat exchanger 5 that exchanges heat between air and the refrigerant. Between the electronic expansion valve 4 and the air heat exchanger 5, the bypath 8 is connected. However, no refrigerant flows through the bypath 8 because the solenoid valve 9 is closed at a time when the hot water system is operated as a water heater.
  • the refrigerant flowing into the air heat exchanger 5 Since the refrigerant flowing into the air heat exchanger 5 is low in temperature, the refrigerant receives heat from the air to evaporate into a low-pressure low-temperature gas refrigerant. In contrast, the air is cooled to low temperature and blows out.
  • the air heat exchanger 5 thus acts as an evaporator of the refrigerating cycle.
  • the low-pressure low-temperature gas refrigerant exiting from the air heat exchanger 5 again flows into the four-way valve 2 for switching the circuit, with which it is fed to the inlet of the compressor 1.
  • the low-pressure low-temperature gas refrigerant fed to the inlet of the compressor 1 is compressed in the compressor 1 into a high-pressure high-temperature gas refrigerant, and is discharged from the outlet.
  • a refrigerant such as R410A for use in air conditioners allows a low-cost refrigerating cycle and increases operation efficiency. For example, when a refrigerant such as CO 2 is used, higher-temperature water can be generated.
  • the air heat exchanger 5 acting as an evaporator is decreased in temperature to 0°C or lower, so that the air that has passed through the air heat exchanger 5 is cooled, and the water in the air is condensed on the surface of the air heat exchanger 5 into frost, thus closing the air path.
  • the operation to remove the frost is generally referred to as a defrosting operation.
  • the reverse-cycle defrosting type hot water system executes the defrosting operation by switching the refrigerating cycle using the four-way valve 2.
  • Fig. 1 shows the flow of the refrigerant in the refrigerating cycle during defrosting operation by broken lines.
  • the high-pressure high-temperature gas refrigerant discharged from the compressor 1 flows into the four-way valve 2.
  • the four-way valve 2 is fixed so as to feed the refrigerant discharged from the compressor 1 to the air heat exchanger 5 that exchanges heat between air and the refrigerant.
  • the high-pressure high-temperature refrigerant fed to the air heat exchanger 5 gives heat to the frost adhered to the air heat exchanger 5 to be condensed.
  • the frost adhered on the air heat exchanger 5 is melted by the heat into liquid and flows down from the air heat exchanger 5.
  • the air heat exchanger 5 acts as a condenser where air and the refrigerant exchange heat.
  • the condensed high-pressure normal-temperature liquid refrigerant is reduced in pressure by the electronic expansion valve 4 into a low-pressure low-temperature liquid refrigerant, and flows into the water heat exchanger 3.
  • the water heat exchanger 3 exchanges heat between the water and the refrigerant, so that the water loses heat to be cooled, while the refrigerant obtains heat to evaporate into a low-pressure low-temperature gas refrigerant.
  • the water heat exchanger 3 acts as an evaporator.
  • the low-pressure low-temperature gas refrigerant discharged from the water heat exchanger 3 again flows into the four-way valve 2 for switching the circuit, and is fed to the inlet of the compressor 1 by the four-way valve 2.
  • the low-pressure low-temperature gas refrigerant fed to the inlet of the compressor 1 is compressed in the compressor 1 into a high-pressure high-temperature gas refrigerant and is discharge from the outlet.
  • the foregoing cycle is repeated to melt the frost adhered to the air heat exchanger 5 into liquid and remove it from the air heat exchanger 5.
  • the water flowing into the water heat exchanger 3 loses heat to be cooled. Since the water discharged from the hot water system is decreased in temperature relative to the water flowing into the hot water system, the hot water system exhibits a negative performance as a water heater.
  • the bypath 8 being disposed so as to redirect the refrigerant from the portion of the pipe 7 in upstream of the electronic expansion valve 4 to the inlet of the compressor 1 during defrosting operation, all the low-pressure low-temperature liquid refrigerant flows into the water heat exchanger 3 acting as an evaporator during defrosting operation. Therefore, the amount of heat exchange between the water and the refrigerant increased, resulting in increased negative performance during the defrosting operation. Moreover, the refrigerant is heated by the heat of the water into a low-pressure low-temperature gas refrigerant.
  • the refrigerant becomes overheated gas and is sucked into the compressor 1.
  • the density of the refrigerant sucked in the compressor 1 during the defrosting operation decreases, thus decreasing the amount of circulation of the refrigerant in the refrigerating cycle.
  • part of the refrigerant flowing in the water heat exchanger 3 acting as an evaporator can be redirected into the inlet of the compressor 1.
  • the amount of the refrigerant flowing through the bypath 8 can be controlled by controlling the degree of opening of the electronic expansion valve 4 in downstream of the inlet of the bypath 8.
  • the degree of opening of the electronic expansion valve 4 is decreased, the amount of the refrigerant flowing to the water heat exchanger 3 decreases, and the refrigerant flowing through the bypath 8 increases.
  • the degree of opening of the electronic expansion valve 4 is increased, the amount of the refrigerant flowing to the water heat exchanger 3 increases, and the refrigerant flowing through the bypath 8 decreases.
  • the refrigerant redirected to the inlet of the compressor 1 through the bypath 8 is mixed with the low-pressure low-temperature gas refrigerant that has passed through the water heat exchanger 3 and is sucked into the compressor 1.
  • the low-pressure low-temperature liquid refrigerant flowing into the water heat exchanger 3 can be decreased, so that the amount of heat exchange between the water and the refrigerant can be decreased, and thus the negative performance during defrosting operation can be reduced.
  • the refrigerant that has become overheated gas by excessive heat exchange is mixed with the normal-temperature liquid refrigerant that has passed through the bypath 8 and sucked into the compressor 1. This increases the density of the refrigerant sucked into the compressor 1 during defrosting operation, resulting in an increase in the amount of circulation of the refrigerant during the refrigerating cycle.
  • the state of the refrigerant to be sucked into the compressor 1 can be controlled by controlling the amount of the refrigerant flowing into the water heat exchanger 3 and the amount of the refrigerant flowing through the bypath 8 by changing the degree of opening of the electronic expansion valve 4 according to the temperature of the refrigerant discharge from the compressor 1.
  • the control of the state of the refrigerant to be sucked into the compressor 1 leads to prevention of abnormal overheating of the compressor 1 by preventing the inflow of an overheated refrigerant and to prevention of damages to the compressor 1 due to the backflow of liquid, thus improving the reliability of the compressor 1.
  • the electronic expansion valve 4 can provide the same advantages as those of the control according to the temperature of the refrigerant discharged from the compressor 1 even if controlled according to either the degree of superheat of the refrigerant sucked in the compressor 1 (degree of inlet superheat) or the degree of superheat of the refrigerant discharged from the compressor 1 (degree of discharge superheat).
  • Fig. 2 is a refrigerant circuit diagram of a hot water system. While the hot water system according to Fig. 1 controls the amount of the refrigerant flowing through the bypath 8 only with the electronic expansion valve 4, the hot water system of Fig. 2 has a bypass electronic expansion valve 10 in series with the solenoid valve 9 in the bypath 8, as shown in Fig. 2 .
  • bypass electronic expansion valve 10 disposed in series with the solenoid valve 9 in the bypath 8 allows controlling the amount of the refrigerant flowing through the bypath 8 with more conditions.
  • the amount of the refrigerant flowing through the bypath 8 is controlled only with the electronic expansion valve 4 during defrosting operation, and the amount of the refrigerant cannot be decreased with the electronic expansion valve 4 which is opened to the maximum, the amount of the refrigerant can be decreased by decreasing the degree of opening of the bypass electronic expansion valve 10.
  • the by pass electronic expansion valve 10 connected in series with the solenoid valve 9 in the bypath 8 may be disposed close to either the inlet or the outlet of the solenoid valve 9 because its action and effect are the same.
  • Fig. 3 is a refrigerant circuit diagram of a hot water system. While the hot water system according to Fig. 1 controls the amount of the refrigerant flowing through the bypath 8 only with the electronic expansion valve 4, the hot water system of Fig. 3 has a capillary 11 in series with the solenoid valve 9 in the bypath 8, as shown in Fig. 3 . Thus, the amount of the refrigerant flowing through the bypath 8 can be reduced, so that the flow rate of the refrigerant flowing through the bypath 8 can be controlled, thereby preventing the refrigerant from flowing into the bypath 8 excessively.
  • This structure allows the amount of the refrigerant flowing through the bypath 8 to be reduced by the capillary 11 during defrosting operation even with the same degree of opening of the electronic expansion valve 4 as that in the case where the amount of the refrigerant is controlled only by the electronic expansion valve 4. This is effective in the case where the refrigerant to be let flow through the bypath 8 may be little.
  • the capillary 11 disposed in series with the solenoid valve 9 in the bypath 8 may be disposed close to either the inlet or the outlet of the solenoid valve 9 because its action and effect are the same.
  • Fig. 4 is a refrigerant circuit diagram of a hot water system according to the invention.
  • the hot water system of Fig. 4 has a receiver 12 disposed between the water heat exchanger 3 and the air heat exchanger 5 in the refrigeration circuit of the hot water system of Fig. 1 , and an additional electronic expansion valve 14 disposed between the receiver 12 and the air heat exchanger 5.
  • the pipe connected to the water heat exchanger 3 is provided with the electronic expansion valve 4
  • the pipe connected to the air heat exchanger 5 is provided with the additional electronic expansion valve 14.
  • the electronic expansion valve 4 is in upstream of the receiver 12 during water heating operation, and controls the refrigerant condensed by the water heat exchanger 3 according to the degree of subcooling.
  • the degree of opening of the electronic expansion valve 4 When the degree of subcooling is low, the degree of opening of the electronic expansion valve 4 is decreased to thereby increase the liquid in the refrigerant condensed by the water heat exchanger 3, thereby increasing the degree of subcooling. In contrast, when the degree of subcooling is high, the degree of opening of the electronic expansion valve 4 is increased to thereby decrease the liquid in the refrigerant condensed by the water heat exchanger 3, thereby decreasing the degree of subcooling.
  • the additional electronic expansion valve 14 is located in downstream of the receiver 12, and controls the refrigerant evaporated by the air heat exchanger 5 according to the degree of superheat.
  • the degree of opening of the additional electronic expansion valve 14 is decreased to thereby decrease the amount of the refrigerant evaporated by the air heat exchanger 5 to increase the degree of dryness of the refrigerant due to evaporation, thereby increasing the degree of superheat.
  • the degree of opening of the additional electronic expansion valve 14 is increased to thereby increase the amount of the refrigerant evaporated by the air heat exchanger 5 to decrease the degree of dryness of the refrigerant due to evaporation, thereby decreasing the degree of superheat.
  • the degree of superheat to be controlled may be either the degree of inlet superheat indicative of the state of the refrigerant sucked in the compressor 1 or the degree of discharge superheat indicative of the state of the refrigerant discharged from the compressor 1 because they offer the same effects.
  • an output temperature that is the temperature of the gas refrigerant discharged from the compressor 1 may be controlled because they offer the same effects.
  • the degree of subcooling of the air heat exchanger 5 is controlled by the additional electronic expansion valve 14 and one of the degree of inlet superheat, the output degree of superheat, and the output temperature of the compressor 1 is controlled by the electronic expansion valve 4.
  • the bypath 8 has therein the solenoid on-off valve 9.
  • the refrigerant flows from a high-pressure portion of the pipeline 7 in upstream of the electronic expansion valve 4 to a low-pressure portion of the pipeline 7 for the inlet of the compressor 1.
  • part of the refrigerant flowing to the water heat exchanger 3 acting as an evaporator can be redirected to the inlet of the compressor 1.
  • the amount of the refrigerant flowing through the bypath 8 can be controlled by controlling the degree of opening of the electronic expansion valve 4 in downstream of the inlet of the bypath 8.
  • the refrigerant redirected to the inlet of the compressor 1 through the bypath 8 is mixed with the low-pressure low-temperature gas refrigerant that has passed through the water heat exchanger 3 and is sucked into the compressor 1.
  • the low-pressure low-temperature liquid refrigerant flowing into the water heat exchanger 3 can be decreased, so that the amount of heat exchange between the water and the refrigerant can be decreased, and thus the negative performance during defrosting operation can be reduced.
  • the refrigerant that has become overheated gas by excessive heat exchange is mixed with the normal-temperature liquid refrigerant that has passed through the bypath 8 and sucked into the compressor 1. This increases the density of the refrigerant sucked into the compressor 1 during defrosting operation, resulting in an increase in the amount of circulation of the refrigerant in the refrigerating cycle.
  • the state of the refrigerant to be sucked into the compressor 1 can be controlled by controlling the amount of the refrigerant flowing into the water heat exchanger 3 and the amount of the refrigerant flowing through the bypath 8 by changing the degree of opening of the electronic expansion valve 4 according to the temperature of the refrigerant discharge from the compressor 1.
  • the control of the state of the refrigerant to be sucked into the compressor 1 leads to prevention of abnormal overheating of the compressor 1 by preventing the inflow of an overheated refrigerant and to prevention of damages to the compressor 1 due to the backflow of liquid, thus improving the reliability of the compressor 1.
  • the electronic expansion valve 4 can provide the same advantages as those of the control according to the temperature of the refrigerant discharged from the compressor 1 even if controlled according to either the degree of inlet superheat of the refrigerant sucked in the compressor 1 or the degree of discharge superheat of the refrigerant discharged from the compressor 1.
  • Fig. 5 is a refrigerant circuit diagram of a hot water system.
  • the hot water system of Fig. 5 has an accumulator 15 disposed between the connection point of the four-way valve 2 and the bypath 8 and the inlet of the compressor 1 in the refrigeration circuit of the hot water system of Fig. 1 . If there is a difference in internal volume between the water heat exchanger 3 and the air heat exchanger 5, a difference may occur between necessary amounts of the refrigerant during water heating operation and defrosting operation, causing excess refrigerant in the refrigerating cycle.
  • the accumulator 15 allows the compressor 1 to suck only the gas refrigerant, preventing the liquid refrigerant to be sucked into the compressor 1, so as to improve the reliability of the compressor 1.
  • part of the refrigerant flowing to the water heat exchanger 3 can be redirected to the inlet of the compressor 1.
  • the amount of the refrigerant flowing through the bypath 8 can be controlled by controlling the degree of opening of the electronic expansion valve 4 in downstream of the inlet of the bypath 8.
  • the refrigerant redirected to the inlet of the compressor 1 through the bypath 8 is mixed with the low-pressure low-temperature gas refrigerant that has passed through the water heat exchanger 3 and is sucked into the compressor 1.
  • the low-pressure low-temperature liquid refrigerant flowing into the water heat exchanger 3 acting as an evaporator can be decreased, so that the amount of heat exchange between the water and the refrigerant can be decreased, and thus the negative performance during defrosting operation can be reduced.
  • the refrigerant that has become overheated gas by excessive heat exchange is mixed with the normal-temperature liquid refrigerant that has passed through the bypath 8 and sucked into the compressor 1. This increases the density of the refrigerant sucked into the compressor 1 during defrosting operation, resulting in an increase in the amount of circulation of the refrigerant in the refrigerating cycle.
  • the state of the refrigerant to be sucked into the compressor 1 can be controlled by controlling the amount of the refrigerant flowing into the water heat exchanger 3 and the amount of the refrigerant flowing through the bypath 8 by changing the degree of opening of the electronic expansion valve 4 according to the temperature of the refrigerant discharge from the compressor 1.
  • the control of the state of the refrigerant to be sucked into the compressor 1 leads to prevention of abnormal overheating of the compressor 1 by preventing the inflow of an overheated refrigerant and to prevention of damages to the compressor 1 due to the backflow of liquid, thus improving the reliability of the compressor 1.
  • the electronic expansion valve 4 can provide the same advantages as those of the control according to the temperature of the refrigerant discharged from the compressor 1 even if controlled according to either the degree of inlet superheat of the refrigerant sucked in the compressor 1 or the degree of discharge superheat of the refrigerant discharged from the compressor 1.
  • Fig. 6 is a refrigerant circuit diagram of a hot water system.
  • a water pump for circulating water is disposed outside the outside unit.
  • the water fed from the water pump flows through a water pipe into the water heat exchanger 3 from the water inlet of the outside unit, exchanges heat with the refrigerant and is fed from the water outlet into the water pipe.
  • a water pump 16 for circulating water is disposed inside an outdoor unit housing 20, as shown in Fig. 6 , so that the water pump 16 can be controlled by the controller of the outside unit.
  • the negative performance can be reduced by stopping the water pump 16 during defrosting operation.
  • the stop of the water pump 16 may cause freezing.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Claims (4)

  1. Système de fourniture d'eau chaude comprenant :
    un compresseur (1) ;
    une vanne à quatre voies (2) destinée à changer le sens du cycle de réfrigération pendant l'opération de dégivrage ;
    un échangeur thermique d'eau (3) destiné à échanger la chaleur entre l'eau et un réfrigérant ;
    une première vanne de détente (4) destinée à réguler la vitesse d'écoulement du réfrigérant pour réduire la pression ; et
    un échangeur thermique d'air (5) destiné à échanger la chaleur entre l'air et le réfrigérant, qui sont raccordés dans cet ordre par une canalisation (7) pour former un cycle de réfrigération permettant de faire circuler le réfrigérant, chauffant ainsi l'eau ;
    le système d'eau chaude comprenant en outre :
    une dérivation (8) destinée à rediriger le réfrigérant provenant d'une partie de la canalisation (7) en amont de la première vanne de détente (4) à l'entrée du compresseur (1) pendant l'opération de dégivrage ; caractérisé par
    une électrovanne (9) disposée dans la dérivation (8), permettant de commuter ;
    un récepteur (12) disposé entre la première vanne de détente (4) et l'échangeur thermique d'air (5) ; et
    une deuxième vanne de détente (14) disposée entre le récepteur (12) et l'échangeur thermique d'air (5),
    la dérivation (8) étant raccordée à une partie de la canalisation (7) entre la première vanne de détente (4) qui est en aval du récepteur (12) pendant l'opération de dégivrage et le récepteur (12), une différence de volume interne existant entre l'échangeur thermique d'eau (3) et l'échangeur thermique d'air (5), et
    lorsque l'électrovanne (9) est ouverte pour rediriger une partie du réfrigérant passant par l'échangeur thermique d'eau (3) jouant le rôle d'évaporateur dans la dérivation (8) pendant l'opération de dégivrage, la quantité de réfrigérant passant par la dérivation (8) étant régulée par le changement du degré d'ouverture de la première vanne de détente (4).
  2. Système de fourniture d'eau chaude selon la revendication 1, dans lequel la dérivation (8) comprend en outre une vanne de détente de dérivation (10) destinée à réguler directement la vitesse d'écoulement du réfrigérant s'écoulant à travers la dérivation (8), installée en série avec l'électrovanne (9).
  3. Système de fourniture d'eau chaude selon la revendication 1, dans lequel la dérivation (8) comprend en outre un capillaire (11) capable de réduire la vitesse d'écoulement du réfrigérant s'écoulant à travers la dérivation (8), disposé en série avec l'électrovanne (9).
  4. Système de fourniture d'eau chaude selon les revendications 1 à 3, dans lequel une pompe (16) destinée à faire circuler l'eau dans le circuit d'eau raccordé à l'échangeur thermique d'eau (3) est disposée dans une unité externe de manière à ce que la pompe (16) ne soit pas arrêtée pendant l'opération de dégivrage.
EP07254439.8A 2007-03-09 2007-11-13 Système de fourniture d'eau chaude Active EP1967801B1 (fr)

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Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4937244B2 (ja) * 2008-12-19 2012-05-23 三菱電機株式会社 ヒートポンプ装置並びにそれを搭載したヒートポンプ給湯機及び空気調和機
JP5427428B2 (ja) 2009-02-06 2014-02-26 三菱重工業株式会社 ヒートポンプ式給湯・空調装置
CN102472540B (zh) * 2009-07-22 2014-07-02 三菱电机株式会社 热泵装置
KR100984305B1 (ko) * 2009-09-10 2010-09-30 에이치에스지(주) 냉온수 히트펌프
WO2011092802A1 (fr) 2010-01-26 2011-08-04 三菱電機株式会社 Dispositif de pompe a chaleur et procede de derivation de fluide frigorigene
KR101169516B1 (ko) 2010-02-04 2012-07-27 엘지전자 주식회사 히트펌프 급탕장치
JP5904628B2 (ja) * 2010-05-26 2016-04-13 サイエンス株式会社 デフロスト運転用の冷媒管を備えた冷凍サイクル
WO2012043379A1 (fr) * 2010-09-29 2012-04-05 東芝キヤリア株式会社 Système d'alimentation en eau chaude
JP5634849B2 (ja) * 2010-12-17 2014-12-03 株式会社不二工機 ロータリ式四方切換弁
JP5765990B2 (ja) * 2011-03-29 2015-08-19 三菱電機株式会社 室内機及び空気調和装置
WO2013008278A1 (fr) * 2011-07-14 2013-01-17 三菱電機株式会社 Dispositif de climatisation
JP5791717B2 (ja) * 2011-07-14 2015-10-07 三菱電機株式会社 空気調和装置
JP5783215B2 (ja) * 2013-09-30 2015-09-24 ダイキン工業株式会社 空気調和装置
JP5988953B2 (ja) * 2013-11-19 2016-09-07 三菱電機株式会社 ヒートポンプ式給湯機
JP6501392B2 (ja) * 2015-02-02 2019-04-17 三菱重工サーマルシステムズ株式会社 制御装置、制御方法及びプログラム
JP6072178B1 (ja) * 2015-09-10 2017-02-01 三菱電機株式会社 冷凍サイクル装置
US10724777B2 (en) * 2015-10-08 2020-07-28 Mitsubishi Electric Corporation Refrigeration cycle apparatus capable of performing refrigerant recovery operation and controlling blower
EP3508802B1 (fr) * 2015-10-20 2020-04-22 Mitsubishi Electric Corporation Appareil de cycle de réfrigération
JP2018096632A (ja) * 2016-12-14 2018-06-21 三菱重工サーマルシステムズ株式会社 冷媒回路システム、制御装置及び制御方法
EP3617616B1 (fr) * 2017-04-27 2023-11-15 Mitsubishi Electric Corporation Dispositif à cycle de réfrigération
CN108007016A (zh) * 2017-10-30 2018-05-08 珠海格力电器股份有限公司 热泵系统以及热泵系统的控制方法
JP7233845B2 (ja) * 2018-03-27 2023-03-07 株式会社富士通ゼネラル 空気調和機
CN110895061A (zh) * 2018-09-12 2020-03-20 艾默生环境优化技术(苏州)有限公司 冷媒循环系统及冷媒循环系统除霜的方法
CN116507865A (zh) * 2020-12-01 2023-07-28 大金工业株式会社 冷冻循环系统
CN117199631A (zh) * 2023-09-21 2023-12-08 无锡启乐智能装备有限公司 一种宽调节范围的直冷直热式电池包控温测试系统

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59131863A (ja) * 1983-01-17 1984-07-28 株式会社東芝 空気調和装置
JPS6158468U (fr) * 1984-09-19 1986-04-19
JPS62162857A (ja) * 1986-01-13 1987-07-18 株式会社東芝 冷凍サイクル装置
JPS62213654A (ja) * 1986-03-14 1987-09-19 株式会社日立製作所 ヒ−トポンプ式冷凍サイクル
JPS6325471A (ja) * 1986-07-17 1988-02-02 三菱電機株式会社 空気調和装置
JPH0633922B2 (ja) * 1986-09-19 1994-05-02 ダイキンプラント株式会社 サ−モタンクを備えた冷凍装置
JPH01114680A (ja) * 1987-10-29 1989-05-08 Sanden Corp ヒートポンプ式冷却装置
JPH0238061U (fr) * 1988-09-03 1990-03-13
JPH02130362A (ja) * 1988-11-11 1990-05-18 Hitachi Ltd 空冷ヒートポンプ式給湯機の除霜制御方法
JPH02197772A (ja) * 1988-12-22 1990-08-06 Daikin Ind Ltd 空気調和機
JPH09257346A (ja) * 1996-03-19 1997-10-03 Mitsubishi Heavy Ind Ltd ヒートポンプ式空気調和機
CN1111689C (zh) * 1997-11-17 2003-06-18 大金工业株式会社 制冷装置
JP4078036B2 (ja) 2001-02-20 2008-04-23 東芝キヤリア株式会社 ヒートポンプ給湯器
CN100504256C (zh) * 2005-03-28 2009-06-24 东芝开利株式会社 热水供给装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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JP4974714B2 (ja) 2012-07-11
JP2008224088A (ja) 2008-09-25
EP1967801A2 (fr) 2008-09-10

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