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EP2645019A1 - Wärmepumpenartige warmwasserversorgungsvorrichtung - Google Patents

Wärmepumpenartige warmwasserversorgungsvorrichtung Download PDF

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Publication number
EP2645019A1
EP2645019A1 EP10859908.5A EP10859908A EP2645019A1 EP 2645019 A1 EP2645019 A1 EP 2645019A1 EP 10859908 A EP10859908 A EP 10859908A EP 2645019 A1 EP2645019 A1 EP 2645019A1
Authority
EP
European Patent Office
Prior art keywords
compressor
pipe
refrigerant
evaporator
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10859908.5A
Other languages
English (en)
French (fr)
Other versions
EP2645019B1 (de
EP2645019A4 (de
Inventor
Takeshi Sugimoto
Masayuki Okazaki
Tomoyoshi Obayashi
Toshiro Abe
Kensuke Inoue
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP2645019A1 publication Critical patent/EP2645019A1/de
Publication of EP2645019A4 publication Critical patent/EP2645019A4/de
Application granted granted Critical
Publication of EP2645019B1 publication Critical patent/EP2645019B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/136—Defrosting or de-icing; Preventing freezing
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/227—Temperature of the refrigerant in heat pump cycles
    • F24H15/232—Temperature of the refrigerant in heat pump cycles at the condenser
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/242—Pressure
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/258—Outdoor temperature
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/305—Control of valves
    • F24H15/32—Control of valves of switching valves
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2007—Arrangement or mounting of control or safety devices for 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
    • 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
    • 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
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0443—Condensers with an integrated receiver the receiver being positioned horizontally
    • 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
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves

Definitions

  • the present invention relates to a heat pump type hot water supply apparatus using a heat pump which circulates a refrigerant, and particularly to a heat pump type hot water supply apparatus which performs a defrosting operation of removing frost attached to a heat exchanger functioning as an evaporator even when an outdoor air temperature is low (for example, 0 degrees C or less).
  • a conventional heat pump type hot water supply apparatus which uses a heat pump for circulating a refrigerant and is capable of performing a defrosting operation for removing frost attached to an evaporator.
  • a method for controlling a heat pump type hot water supply apparatus having a refrigeration cycle which includes a water heat exchanger that heats water to generate hot water, wherein if an outside air temperature is lower than or equal to a predetermined temperature, a preset high limit temperature of hot water generated by the water heat exchanger is regulated has been proposed (for example, refer to Patent Literature 1).
  • a defrosting operation is carried out in which by conducting a refrigerant (hot gas) discharged from a compressor into a heat source side heat exchanger, frost attached to the heat source side heat exchanger is melted.
  • a refrigerant hot gas
  • frost attached to the heat source side heat exchanger is melted.
  • a water heat exchanger may be in danger of freezing when the water temperature becomes low or if the temperature of the water heat exchanger becomes lower.
  • a bypass circuit so as to prevent a refrigerant from flowing into the water heat exchanger, or by letting the refrigerant to flow into the bypass circuit in parallel to the water heat exchanger so as to reduce an amount of the refrigerant circulating in the water heat exchanger, freezing of the water heat exchanger is prevented.
  • a predetermined temperature for example, -5 degrees C
  • a desired high limit temperature of hot water is decreased (for example, the temperature is lowered from 65degrees C to 58degrees C).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2009-41860 (refer to page7, Fig. 1 and the like)
  • Patent Literature 1 The technology described in Patent Literature 1 is established for the purpose of reducing the load for a compressor, such that if the outside air temperature becomes lower than or equal to a predetermined temperature, a preset high limit temperature of hot water generated by a water heat exchanger is regulated. This lowers the hot water temperature in a hot water storage tank below 60 degrees C, and therefore, there is a possibility that the hot water temperature in the hot water storage tank cannot be maintained at 60 degrees C that is required for preventing outbreak of Legionaires' disease.
  • the recommended temperature of hot water stored in the hot water storage tank so as to suppress bleeding of Legionella bacteria is 60 degrees C or higher.
  • the invention has been made to overcome the above-described problems, and an object of the invention is to provide a heat pump type hot water supply apparatus which can maintain the hot water temperature (for example, 65degrees C) required even when the outside air temperature is low (for example, when the outside air temperature is 0degrees C or less) and perform a defrosting operation of an evaporator with high efficiency.
  • the hot water temperature for example, 65degrees C
  • the outside air temperature for example, when the outside air temperature is 0degrees C or less
  • a heat pump type hot water supply apparatus includes a main circuit in which a compressor, a flow switching device, a water heat exchanger, an expansion device and an evaporator are connected by pipes, and this apparatus performs a reverse defrosting operation in which a refrigerant discharged from the compressor is made to flow into the evaporator by switching the flow of the refrigerant by the flow switching device. Further, this apparatus performs the reverse defrosting operation in which the refrigerant discharged from the compressor is conducted to passes other than a pass located at a lower portion of the evaporator.
  • the refrigerant discharged from the compressor is branched off between the compressor and the flow switching device, and is conducted to the pass located at the lower portion of the evaporator such that the refrigerant flows in parallel to the water heat exchanger until the predetermined time has elapsed.
  • a heat pump type hot water supply apparatus is configured such that, after completion of a reverse defrosting operation, when an outside air temperature is a predetermined temperature or less and thereafter a predetermined time has elapsed or a difference between a compressor shell temperature and a low pressure saturation temperature becomes a predetermined value or less, a refrigerant discharged from a compressor is branched off between the compressor and a flow switching device, and is conducted to a pass located at a lower portion of the evaporator such that the refrigerant flows in parallel to a water heat exchanger until the predetermined time has elapsed.
  • the hot water temperature (for example, 65 degrees C) which is required even when the outside air temperature is low can be maintained, and at the time of a hot water supply operation, and it becomes possible to prevent the refrigerant from being stored in the pass located in the lower portion of the evaporator, and thus this apparatus can perform the defrosting operation with high efficiency without decreasing a heating capacity for removing frost which is caused by a refrigerant shortage during the defrosting operation.
  • Fig. 1 is a refrigerant circuit diagram illustrating an exemplary refrigerant circuit configuration of a heat pump type hot water supply apparatus 100 according to Embodiment of the invention.
  • the heat pump type hot water supply apparatus 100 is configured to perform a hot water supply operation by use of a refrigeration cycle for circulating a refrigerant (a heat pump cycle).
  • a refrigeration cycle for circulating a refrigerant a heat pump cycle
  • the heat pump type hot water supply apparatus 100 is provided with a refrigerant circuit, as a main circuit, in which a compressor 1, a four-way valve 2 serving as a flow switching valve, a water heat exchanger 3 (for example, a load side heat exchanger which exchanges heat between a refrigerant circulating in the refrigerant circuit and a heat medium such as water circulating in a water circuit), a liquid receiver 6, a double pipe heat exchanger 7, an expansion device 11, and an evaporator 13 are connected by a refrigerant pipe 20. That is to say, due to the refrigerant being circulated in the main circuit, the heat pump type hot water supply apparatus 100 can be configured to perform a hot water supply operation.
  • a compressor 1 a four-way valve 2 serving as a flow switching valve
  • a water heat exchanger 3 for example, a load side heat exchanger which exchanges heat between a refrigerant circulating in the refrigerant circuit and a heat medium such as water circulating in a water circuit
  • the heat pump type hot water supply apparatus 100 includes an injection pipe 21 formed by branching off a liquid pipe at an outlet side of the liquid receiver 6 and connecting the pipe to the compressor 1 via a secondary side of the double pipe heat exchanger 7. As a result, it becomes possible to suppress decrease of the heating capacity of the apparatus in a cold district as well.
  • An injection electronic expansion valve 8 is provided between a branch point of the injection pipe 21 and the double pipe heat exchanger 7.
  • An injection solenoid valve 9 is provided on the injection pipe 21 between the double pipe heat exchanger 7 and the compressor 1.
  • the heat pump type hot water supply apparatus device 100 includes a first bypass pipe 23 formed by branching off the refrigerant pipe 20 at an outlet side of the water heat exchanger 3 and connected to an outlet side of the double pipe heat exchanger 7.
  • the first bypass pipe 23 is provided with a first check valve 10.
  • the heat pump type hot water supply apparatus 100 includes a second bypass pipe 24 which bypasses the expansion device 11.
  • the second bypass pipe 24 is provided with a second check valve 12.
  • the heat pump type hot water supply apparatus 100 also includes a hot gas conducting pipe 22 used to conduct a refrigerant (hot gas) discharged from the compressor 1 to the evaporator 13.
  • the hot gas conducting pipe 22 is provided with a hot gas solenoid valve 14.
  • a high pressure sensor 15 is provided in a discharge portion of the compressor 1
  • a low pressure sensor 16 is provided in a suction portion of the compressor 1
  • a shell temperature sensor 17 is provided in a lower portion of the compressor 1
  • an outside air temperature sensor 18 is provided in the vicinity of the evaporator 13.
  • the compressor 1 is used to compress a refrigerant suctioned from the suction portion, the injection pipe 21 and the hot gas conducting pipe 22 into a high temperature, high pressure state.
  • the compressor 1 may be, for example, a capacity controllable compressor of which rotation speed can be controlled by an inverter.
  • the compressor 1 is configured so as to be capable of injecting the refrigerant passing through the injection pipe 21 into a compression chamber inside of the compressor 1. Further, the compressor 1 is also configured so as to be capable of letting the refrigerant passing through the hot gas conducting pipe 22 flow into the compression chamber of the compressor 1.
  • the four-way valve 2 is used to switch the flow direction of the refrigerant between the reverse defrosting operation and the hot water supply operation.
  • the water heat exchanger 3 is used to receive and pass heating energy stored in the refrigerant to a water circuit side.
  • An inlet of a water circuit connected to the water heat exchanger 3 is referred to as a water circuit inlet 4, and an outlet of the water circuit is referred to as a water circuit outlet 5.
  • the water circuit inlet 4 and the water circuit outlet 5 are each connected to a hot water storage tank, which is not illustrated, and thereby form the water circuit.
  • the hot water storage tank is configured to store therein hot water boiled by the water heat exchanger 3.
  • the liquid receiver 6 is provided at the outlet side of the water heat exchanger 3 and is used to store therein excess refrigerant.
  • the heat is exchanged between the refrigerant flowing out from the double pipe heat exchanger 7 and from the liquid receiver 6 and passing through the injection pipe 21, and the refrigerant flowing through the refrigerant pipe 20.
  • the double pipe heat exchanger 7 is formed by a liquid pipe (referred to as a liquid pipe 20a) through which a liquid refrigerant flowing out from the liquid receiver 6 passes, the injection pipe 21 of which pipe diameter is larger than that of the liquid pipe 20a and which is disposed so as to cover the liquid pipe 20a, and a pipe unit (not illustrated) of which pipe diameter is larger than that of the injection pipe 21 and which forms an enclosed space.
  • the liquid pipe 20a side of the double pipe heat exchanger 7 is referred to as a primary side
  • the injection pipe 21 side thereof is referred to as a secondary side.
  • the expansion device 11 serves as a reducing valve or an expansion valve and is used to decompress and expand a refrigerant.
  • the expansion device 11 may be, for example, an electronic expansion valve having a variably controllable opening degree.
  • the evaporator 13 exchanges heat between air (outside air) supplied from a fan which is not illustrated or the like, and the refrigerant, so as to evaporate and gasify the refrigerant.
  • the refrigerant pipe 20 is used to link various component devices.
  • Each of the liquid pipe 20a, the injection pipe 21, the hot gas conducting pipe 22, the first bypass pipe 23, and the second bypass pipe 24 is a component which forms a part of the refrigerant pipe 20.
  • the injection electronic expansion valve 8 is used to decompress and expand the refrigerant flowing through the injection pipe 21.
  • the injection electronic expansion valve 8 may be, for example, an electronic expansion valve having a variably controllable opening degree.
  • the injection solenoid valve 9 is controlled so as to open and close and is used to control flowing of the refrigerant into the injection pipe 21.
  • the first check valve 10 permits the flow of the refrigerant in one direction (from the expansion device 11 to the water heat exchanger 3 side).
  • the second check valve 12 permits the flow of the refrigerant in one direction (from the evaporator 13 to the inlet side of the first bypass pipe 23).
  • the hot gas solenoid valve 14 is controlled so as to open and close, and is used to control flowing of the refrigerant into the hot gas conducting pipe 22.
  • the high pressure sensor 15 is used to detect the pressure of the refrigerant discharged from the compressor 1.
  • the low pressure sensor 16 is used to detect the pressure of the refrigerant to be suctioned into the compressor 1.
  • the shell temperature sensor 17 is used to detect the shell temperature of the compressor 1.
  • the outside air temperature sensor 18 is used to detect the temperature of outside air which exchanges heat with the evaporator 13. Information detected by these sensors (pressure information, temperature information) is transmitted to a controller 50 and is used for a driving frequency of the compressor 1, switching of the four-way valve 2, the opening degree of the expansion device 11, the opening degree of the injection electronic expansion valve 8, opening and closing of the injection solenoid valve 9, opening and closing of the hot gas solenoid valve 14, and the like.
  • Fig. 2 is a schematic diagram illustrating an exemplary pass pattern of the evaporator 13 of the heat pump type hot water supply apparatus 100.
  • the evaporator 13 will be further described below in detail.
  • the evaporator 13 is configured in such a manner that the refrigerant is branched off at an inlet header 31 provided at an inlet side of the evaporator and flows into plural passes, and the refrigerant which has flowed out of the plural passes is merged at an outlet header 32 provided at the outlet side of the evaporator.
  • Fig. 2 illustrates a state in which the pass of the evaporator 13 is branched into eight ways, that is, passes 30a to 30h.
  • a pass 33 located at the lowermost position of the evaporator 13 does not communicate with the other passes (the passes 31 a to 31 h). In other words, the pass 33 does not communicate with the inlet header 31 or with the outlet header 32.
  • the pass 33 is configured in such a manner that the inlet side thereof is made to communicate with the hot gas solenoid valve 14 and the outlet side thereof is made to communicate with the suction portion of the compressor 1 via another pipe (the hot gas conducting pipe 22). Accordingly, the hot gas solenoid valve 14 is controlled so as to close during the water heating operation (at the time of the heating operation), and therefore, the refrigerant does not flow in the pass 33.
  • a unit base 34 is provided at a lower side of the evaporator 13.
  • the evaporator 13 is disposed above the unit base 34.
  • Fig. 2 as a suitable example, a case in which the pass 33 located at the lowermost position alone does not communicate with the other passes (the passes 31 a to 31 h) is shown.
  • a plurality of passes disposed at the lower portion of the evaporator 13 each may be made to function as in the pass 33.
  • the refrigerant circulating in the refrigerant circuit which constitutes the heat pump type hot water supply apparatus 100 for example, a single refrigerant such as R-22, R-134a, R-32, a near-azeotropic refrigerant mixture such as R-410A, R-404A, a non-azeotropic refrigerant mixture such as R-407C, tetrafluoropropene (HFO-1234yf or HFO-1234ze) that is a refrigerant which contains a double bond in its chemical formula and is expressed in the chemical formula C3H2F4 and has a relatively low global warming potential, a mixture containing the refrigerant, or a natural refrigerant, such as CO2 or propane, can be used.
  • a single refrigerant such as R-22, R-134a, R-32
  • a near-azeotropic refrigerant mixture such as R-410A, R-404A
  • a non-azeotropic refrigerant mixture
  • R-32 having a low global warming potential or, for example, a refrigerant mixture containing R-32 and tetrafluoropropene (HFO-1234yf or HFO-1234ze).
  • HFO-1234yf a refrigerant mixture containing R-32 and tetrafluoropropene
  • refrigerants such as R407C, R134a, HFO-1234yf, HFO-1234ze are particularly preferable.
  • the refrigerant discharged from the compressor 1 is made to flow via the four-way valve 2 to the water heat exchanger 3.
  • the refrigerant which has flowed into the water heat exchanger 3 exchanges heat with a heat medium such as water which has flowed from the water circuit inlet 4, and heats the water.
  • the heated heat medium in this case, hot water
  • the pipe from the hot water storage tank communicates with the water circuit inlet 4, and therefore, the heat medium circulates between the water heat exchanger 3 and the hot water storage tank.
  • the refrigerant that has heated the heat medium flows out from the water heat exchanger 3 and passes through the liquid receiver 6, and thereafter, is branched off. A part of the refrigerant flows into the liquid pipe 20a and the remaining part thereof flows into the injection pipe 21.
  • the double pipe heat exchanger 7 exchanges heat between the primary side refrigerant flowing through the liquid pipe 20a, and the secondary side refrigerant flowing in the injection pipe 21 and pressed by the injection electronic expansion valve 8. In other words, the double pipe heat exchanger 7 exchanges heat between the refrigerant flowing through the liquid pipe 20a led to a closed space, and the refrigerant flowing through the injection pipe 21. Then, the liquid refrigerant subcooled by the secondary side refrigerant is conducted to the expansion device 11, and thereafter, it flows into the evaporator 13.
  • the refrigerant passes through the passes 30a to 30h other than the lowermost pass 33, and exchanges heat with the outside air.
  • the refrigerant which has exchanged heat with the outside air is made to merge at the outlet header 32, and is again suctioned into the compressor 1 via the four-way valve 2.
  • the hot gas solenoid valve 14 is controlled so as to close, so that the refrigerant does not flow into the pass 33 located at the lowermost position of the evaporator 13.
  • the refrigerant which has flowed into the injection pipe 21 passes through the injection electronic expansion valve 8, and thereafter, exchanges heat with the liquid refrigerant at the primary side in the double pipe heat exchanger 7.
  • the refrigerant flows out of the double pipe heat exchanger 7, and thereafter, flows through the injection solenoid valve 9 which is controlled so as to open when the injection is required, and is further made to flow to an intermediate portion (an injection port) of the compression chamber in the compressor 1, thereby cooling gas discharged from the compressor 1.
  • frost is attached to the evaporator 13. If the frost attached to the evaporator 13 is left as it is, the heat exchange capacity of the evaporator 13 may become degraded. In this case, a desired capacity of the hot water supply operation cannot be exhibited. Accordingly, in the heat pump type hot water supply apparatus 100, a defrosting operation for removing frost attached to the evaporator 13 is appropriately performed.
  • the defrosting operation performed by the heat pump type hot water supply apparatus 100 there are two types of operation as follows: a reverse defrosting operation in which the refrigerant flow is reversed so that the refrigerant discharged from the compressor 1 is made to flow into the evaporator 13; and a hot gas defrosting operation in which a part of the refrigerant (hot gas) discharged from the compressor 1 is branched off and is made to flow into the evaporator 13.
  • the defrosting operation will be described below in detail.
  • the refrigerant discharged from the compressor 1 is led to the evaporator 13 by switching the four-way valve 2.
  • the refrigerant passes through the passes 30a to 30h other than the pass 33, and frost attached to the evaporator 13 is melted.
  • the refrigerant which has exchanged heat with the frost attached to the evaporator 13 is merged at the outlet header 32, and flows in the second bypass pipe 24 and the first bypass pipe 23, and bypasses the expansion device 11, and the double pipe heat exchanger 7 and the liquid receiver 6, respectively, and also passes through the water heat exchanger 3, and is suctioned again into the compressor 1 via the four-way valve 2.
  • the heat medium is circulated in the water heat exchanger 3, so as not to be frozen.
  • the hot gas defrosting operation can be performed by controlling the hot gas solenoid valve 14 to be open.
  • the refrigerant thus can be made to flow into the hot gas conducting pipe 22 in parallel with the refrigerant circuit for the hot water supply operation.
  • a part of the refrigerant discharged from the compressor 1 is branched off from between the compressor 1 and the four-way valve 2, and flows into the pass 33 located at the lowermost position of the evaporator 13 via the hot gas solenoid valve 14.
  • Another part of the refrigerant discharged from the compressor 1 flows into the water heat exchanger 3 via the four-way valve 2.
  • the refrigerant which has flowed into the pass 33 exchanges heat with the frost attached to the lowermost position of the evaporator 13, and thereafter, flows from the evaporator 13 and is led to the suction side of the compressor 1.
  • Fig. 3 is a flow chart showing the flow of a control operation during the defrosting operation (the reverse defrost operation and the hot gas defrosting operation).
  • the controller 50 starts the defrosting operation when it is determined that predetermined conditions (for example, a cumulative operation time of the compressor 1, a drop in the outside air temperature, and the like) have been satisfied (step S101).
  • the controller 50 performs the reverse defrosting operation by, at first, switching the four-way valve 2 to flow hot gas into the passes 30a to 30h of the evaporator 13 (step S102).
  • the controller 50 terminates the reverse defrosting operation (step S103). Subsequently, the controller makes a determination as to whether the outside air is lower than or equal to a predetermined temperature (for example, 0 degrees C or less) (step S104). When the outside air is not less than or equal to the predetermined temperature (step S104: NO), the controller 50 switches the four-way valve 2 and performs the hot water supply operation (step S110).
  • a predetermined temperature for example, 0 degrees C or less
  • step S104 when the outside air is less than or equal to the predetermined temperature (step S104: YES), the controller 50 is in a standby state until a predetermined time (for example, 10 seconds) elapses after completion of the reverse defrosting operation (step S105).
  • a predetermined time for example, 10 seconds
  • the controller 50 controls the hot gas solenoid valve 14 to be open, and starts the hot gas defrosting operation (step S106).
  • the reason for the controller 50 to be in a standby state for the predetermined time is so that, when the four-way valve 2 is switched after completion of the reverse defrosting operation, the controller 50 can change to the hot gas defrosting operation after the four-way valve 2 is reliably switched by the pressure difference between the front and rear sides of the four-way valve 2.
  • the controller 50 makes a determination as to whether a predetermined time (for example, five minutes or thereabouts) has elapsed after the start of the hot gas defrosting operation (step S107).
  • a predetermined time for example, five minutes or thereabouts
  • the controller 50 finishes the hot gas defrosting operation (step S108), and controls the hot gas solenoid valve 14 to be closed and switches to the hot water supply operation (step S110).
  • step S107 determines that the predetermined time has not elapsed after the start of the hot gas defrosting operation.
  • the controller 50 converts the shell temperature of the compressor 1 detected by the shell temperature sensor 17 and the low pressure value detected by the low pressure sensor 16 into a low pressure saturated gas temperature, and makes a determination as to whether a value (given by subtracting the low pressure saturated gas temperature from the compressor shell temperature) is a predetermined value or less (step S109).
  • step S109 NO
  • the controller 50 returns to a determination as to whether the predetermined time has elapsed after the start of the hot gas defrosting operation (step S107).
  • step S109: YES when it is determined that the value (given by subtracting the low pressure saturated gas temperature from the compressor shell temperature) is the predetermined value or less (step S109: YES), the controller 50 makes a determination that the refrigerant may return to the compressor in a liquid state, and even when the predetermined time has not elapsed after the start of the hot gas defrosting operation, the hot gas defrosting operation is finished so as to protect the compressor 1 (step S108). Then, the controller controls the hot gas solenoid valve 14 to be closed and switches to the hot water supply operation (step S110).
  • the refrigerant may be accumulated in the pass 33 located at the lowermost position of the evaporator 13. In such cases, the refrigerant cannot be used at the defrosting operation, the amount of refrigerant therefore becomes insufficient and the heating capacity may become degraded. Further, the pass 33 located at the lowermost position of the evaporator 13 is provided in the vicinity of the unit base 34, and therefore, snow piled in the unit base 34 or the cold unit base 34 draws heat required for removing frost during the defrosting operation.
  • the evaporator 13 is configured such that the pass 33 located at the lowermost position in the vicinity of the unit base 34 is separated from the other passes 30a to 30h. Accordingly, during the hot water supply operation, the refrigerant is not allowed to be accumulated in the pass 33 located at the lowermost position of the evaporator 13, thereby making it possible to prevent deterioration of the heating capacity for removing frost caused by the refrigerant shortage during the defrosting operation. Further, even when the outside air temperature is low, deterioration of the hot water supplying ability can be suppressed and the hot water supplying temperature can be maintained at a high value (for example, 65degrees C). Accordingly, breeding of Legionella bacteria or the like in the hot water storage tank can be suppressed.
  • a high value for example, 65degrees C
  • the heat pump type hot water supply apparatus 100 is configured to perform the reverse defrosting operation via the passes 30a to 30h of the evaporator 13 and thereafter, let the hot gas flow into the pass 33 located at the lowermost position of the evaporator 13. Accordingly, at the time of defrosting in the other passes than the pass 33 located at the lowermost position of the evaporator 13, the hot gas defrosting operation can be performed without excessively heating water which has been generated by melting frost by the reverse defrosting operation and has dropped down in the pass 33, and also without letting the dropped water deprive of the heating capacity. For this reason, by the hot gas defrosting operation, it becomes possible to reliably remove frost from the part in the vicinity of the unit base 34 and the lower portion of the evaporator 13 which could be a source of remaining ice.
  • Fig. 4 is a refrigerant circuit diagram illustrating another exemplary refrigerant circuit configuration of the heat pump type hot water supply apparatus according to Embodiment of the invention. With reference to Fig. 4 , another exemplary circuit configuration of the heat pump type hot water supply apparatus 100 will be described below.
  • a first hot gas expansion device 25 is provided between the compressor 1 and the hot gas solenoid valve 14, and a second hot gas expansion device 26 is provided between the pass 33 of the evaporator 13 and a suction port of the compressor 1.
  • Fig. 4 illustrates a case in which the first hot gas expansion device 25 and the second hot gas expansion device 26 each includes a capillary, but the configuration is not limited to this case. These expansion devices each may also be an expansion device such as an expansion valve.
  • the refrigerant to be used, the number of the water heat exchangers 3, the respective number of the temperature sensors and pressure sensors may also be determined in accordance with intended purposes and uses for which the heat pump type hot water supply apparatus 100 is applied.
  • the controller 50 may be configured by a microcomputer or the like, which is capable of performing the integrated control of the heat pump type hot water supply apparatus 100.

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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)
EP10859908.5A 2010-11-24 2010-11-24 Wärmepumpenartige warmwasserversorgungsvorrichtung Active EP2645019B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/006840 WO2012070082A1 (ja) 2010-11-24 2010-11-24 ヒートポンプ式給湯装置

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EP2645019A1 true EP2645019A1 (de) 2013-10-02
EP2645019A4 EP2645019A4 (de) 2014-05-07
EP2645019B1 EP2645019B1 (de) 2020-10-28

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2827081A3 (de) * 2013-07-16 2015-04-15 Robert Bosch Gmbh Verfahren zum Steuern einer Wärmepumpe
CN106595116A (zh) * 2016-12-23 2017-04-26 Tcl空调器(中山)有限公司 空调器及其控制方法
CN113294945A (zh) * 2020-02-21 2021-08-24 (株)Ptc 半导体工艺用冷却装置
CN113348333A (zh) * 2019-02-05 2021-09-03 三菱电机株式会社 制冷装置的室外机以及具备该室外机的制冷装置

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JP2014013121A (ja) * 2012-07-05 2014-01-23 Panasonic Corp 空気調和機
EP2940407B1 (de) * 2012-12-26 2018-11-14 Daikin Industries, Ltd. Wärmepumpenwarmwasserbereiter
CN105698382B (zh) * 2016-03-14 2018-03-30 广东美的制冷设备有限公司 热泵热水器及其控制方法
CN108954675A (zh) * 2018-07-17 2018-12-07 苏州韵之秋智能科技有限公司 一种不停机化霜智能空调
CN112137542B (zh) * 2019-06-27 2024-07-30 青岛海尔洗碗机有限公司 一种洗碗机及控制方法
KR20210100461A (ko) * 2020-02-06 2021-08-17 엘지전자 주식회사 공기 조화 장치

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JPH09329387A (ja) * 1996-06-07 1997-12-22 Sanyo Electric Co Ltd 冷却装置
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Cited By (5)

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Publication number Priority date Publication date Assignee Title
EP2827081A3 (de) * 2013-07-16 2015-04-15 Robert Bosch Gmbh Verfahren zum Steuern einer Wärmepumpe
CN106595116A (zh) * 2016-12-23 2017-04-26 Tcl空调器(中山)有限公司 空调器及其控制方法
CN113348333A (zh) * 2019-02-05 2021-09-03 三菱电机株式会社 制冷装置的室外机以及具备该室外机的制冷装置
EP3922928A4 (de) * 2019-02-05 2022-01-26 Mitsubishi Electric Corporation Ausseneinheit einer kühlvorrichtung und kühlvorrichtung damit
CN113294945A (zh) * 2020-02-21 2021-08-24 (株)Ptc 半导体工艺用冷却装置

Also Published As

Publication number Publication date
EP2645019B1 (de) 2020-10-28
WO2012070082A1 (ja) 2012-05-31
JP5653451B2 (ja) 2015-01-14
EP2645019A4 (de) 2014-05-07
JPWO2012070082A1 (ja) 2014-05-19

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