EP2759787B1 - Wärmepumpenvorrichtung - Google Patents

Wärmepumpenvorrichtung Download PDF

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Publication number
EP2759787B1
EP2759787B1 EP12832013.2A EP12832013A EP2759787B1 EP 2759787 B1 EP2759787 B1 EP 2759787B1 EP 12832013 A EP12832013 A EP 12832013A EP 2759787 B1 EP2759787 B1 EP 2759787B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
circuit
valve
intermediate heat
Prior art date
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Application number
EP12832013.2A
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English (en)
French (fr)
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EP2759787A4 (de
EP2759787A1 (de
Inventor
Takashi Okazaki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2759787A4 publication Critical patent/EP2759787A4/de
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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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary 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
    • F25B39/00—Evaporators; 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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/32—Responding to malfunctions or emergencies
    • F24F11/36—Responding to malfunctions or emergencies to leakage of heat-exchange fluid
    • 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
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • 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
    • F25B2400/06—Several compression cycles arranged in parallel
    • 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
    • F25B2400/12—Inflammable refrigerants
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
    • F25B2500/222—Detecting refrigerant leaks

Definitions

  • the present invention relates to a technique for securing safety when a refrigerant leaks from a heat pump apparatus.
  • An air-conditioning apparatus (an example of a heat pump apparatus) which utilizes a refrigeration cycle technique using a refrigerant as a way of cooling, heating, or dehumidifying a room.
  • Fluorine compounds such as R410A that is hydrofluorocarbon (HFC) are widely used as refrigerants in air-conditioning apparatuses. These refrigerants, however, have a considerable impact on global warming. In terms of prevention of global warming, therefore, it is desirable to use refrigerants having a less impact on global warming. Accordingly, the use of refrigerants having a less impact on global warming, such as R32 that is HFC, R1234yf that is hydrofluoro-olefin (HFO), propane and isobutene that are hydrocarbons, has been proposed. Disadvantageously, all of these refrigerants are flammable, unlike the conventional refrigerants.
  • HFC hydrofluorocarbon
  • the refrigerant may leak from a heat exchanger, a pipe, or the like included in a refrigeration cycle and an explosive atmosphere may accordingly be produced in a room. This may lead to an accident, such as fire.
  • Patent Literature 1 discloses an air-conditioning apparatus that addresses the above-described problem.
  • This air-conditioning apparatus is of an indirect type including a primary circuit through which a flammable refrigerant is circulated and a secondary circuit through which a nonflammable heat medium is circulated.
  • the heat medium circulated through the secondary circuit is heated or cooled by the flammable refrigerant circulated through the primary circuit, the flammable refrigerant circulated through the primary circuit is not permitted to flow to a room, and only the heat medium circulated through the secondary circuit is permitted to flow to the room.
  • the indirect air-conditioning apparatus prevents the flammable refrigerant from flowing to the room, thus preventing the room from being in an explosive atmosphere.
  • JP 2010 256009 A discloses a heat pump apparatus according to the preamble of claim 1.
  • a first circuit of a circulation conduit is connected to the first refrigerating machine that is an ammonia absorbing type refrigerating machine.
  • a sending-out conduit includes a first blocking valve and a returning conduit includes a second blocking valve.
  • An ammonia detection device is connected to the sending-out conduit. The ammonia detection device takes a part of the brine flowing in the sending-out conduit. When the ammonia detection device detects ammonia in the brine which it has taken, the first blocking valve and the second blocking valve are blocked-off.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2009-150620
  • a plate heat exchanger or a double pipe heat exchanger is used as an intermediate heat exchanger that exchanges heat between the flammable refrigerant circulated through the primary circuit and the heat medium circulated through the secondary circuit.
  • the intermediate heat exchanger may be damaged due to freezing or deterioration over time.
  • a passage in the primary circuit may communicate with a passage in the secondary circuit, thus allowing the flammable refrigerant circulated through the primary circuit to mix with the heat medium circulated through the secondary circuit.
  • the heat medium containing the flammable refrigerant may leak into a room from a welded seam or joint of pipes included in the secondary circuit.
  • a primary object of the present invention is to prevent a refrigerant in a primary circuit from leaking through a secondary circuit in a heat pump apparatus that uses an indirect system including the primary circuit on a heat source side and the secondary circuit on a load side.
  • the present invention provides a heat pump apparatus according to claim 1.
  • the heat pump apparatus closes the first valve and the second valve when the refrigerant leaks from the first refrigerant circuit, serving as a primary circuit, into the fluid circuit, serving as a secondary circuit, thus preventing the refrigerant circulated through the primary circuit from flowing beyond the first valve and the second valve in the secondary circuit.
  • the refrigerant circulated through the primary circuit can be prevented from leaking beyond the first valve and the second valve in the secondary circuit to the outside.
  • Fig. 1 is a diagram illustrating the configuration of an air-conditioning apparatus 100 according to Embodiment 1.
  • each blanked arrow indicates the flow of air and each dotted arrow indicates the flow of a signal.
  • the air-conditioning apparatus 100 includes a refrigerant circuit 6 (first refrigerant circuit or primary circuit) that includes a compressor 1 (first compressor), a four-way valve 2, a heat exchanger 3 (first heat exchanger), an expansion valve 4 (first expansion mechanism), an intermediate heat exchanger 5 (first intermediate heat exchanger) sequentially connected in loop by pipes.
  • the air-conditioning apparatus 100 further includes a water circuit 10 (fluid circuit or secondary circuit) that includes the intermediate heat exchanger 5, a pump 7, a valve 8a (first valve), a heat exchanger 9 (load heat exchanger), and a valve 8b (second valve) sequentially connected in loop by pipes.
  • a flammable refrigerant such as a propane or isobutane, having a lower liquid density (liquid head) than water is circulated through the refrigerant circuit 6 and water is circulated through the water circuit 10.
  • a fan 11 that delivers airflow to the heat exchanger 3 is disposed near the heat exchanger 3.
  • a fan 12 that delivers airflow to the heat exchanger 9 is disposed near the heat exchanger 9.
  • the air-conditioning apparatus 100 further includes a leakage detecting device 13 that detects leakage of the refrigerant, circulated through the refrigerant circuit 6, from the intermediate heat exchanger 5 into the water circuit 10 and a controller 14 that closes the valves 8a and 8b when the leakage detecting device 13 detects the leakage of the refrigerant.
  • the compressor 1, the four-way valve 2, the heat exchanger 3, the expansion valve 4, the intermediate heat exchanger 5, the pump 7, the valves 8a and 8b, the fan 11, the leakage detecting device 13, and the controller 14 of the components included in the air-conditioning apparatus 100 are accommodated in an outdoor unit 15 (first casing) installed outside a room.
  • the heat exchanger 9 and the fan 12 of the components included in the air-conditioning apparatus 100 are accommodated in an indoor unit 16 (second casing) installed inside the room.
  • the intermediate heat exchanger 5 is a plate heat exchanger or double pipe heat exchanger that has high efficiency of heat exchange.
  • the pump 7 is a pump having a variable rotation speed.
  • the valve 8a is a valve that includes a variable expansion mechanism capable of controlling an opening degree.
  • the valve 8b is a valve that performs a simple opening and closing operation.
  • the leakage detecting device 13 detects a pressure in the water circuit 10 using a pressure sensor to detect leakage of the refrigerant.
  • the leakage detecting device 13 detects, in particular, a pressure at a point between the pump 7 and the valve 8a to detect the leakage of the refrigerant.
  • the controller 14 is a microcomputer.
  • Fig. 2 is a diagram illustrating the flow of the refrigerant and that of the water during the cooling operation in the air-conditioning apparatus 100 according to Embodiment 1.
  • solid line arrows indicate the flow of the refrigerant and broken line arrows indicate the flow of the water.
  • the four-way valve 2 is set so as to provide passages indicated by solid lines illustrated in Fig. 1 .
  • An opening degree of the valve 8a is set in such a manner that the water flows at a constant rate.
  • the valve 8b is opened. Controlling the flow rate of the water flowing through the valve 8a controls the amount of heat exchange in the heat exchanger 9.
  • a high-temperature high-pressure refrigerant, obtained by the compressor 1, passes through the four-way valve 2 and flows into the heat exchanger 3.
  • the refrigerant, which has flowed into the heat exchanger 3, exchanges heat with outdoor air, so that the refrigerant condenses into a liquid refrigerant.
  • the liquid refrigerant passes through the expansion valve 4 where the refrigerant is expanded into a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the intermediate heat exchanger 5 and exchanges heat with the water circulated through the water circuit 10, so that the refrigerant evaporates into a gas refrigerant.
  • the water circulated through the water circuit 10 is cooled.
  • the gas refrigerant passes through the four-way valve 2 and is sucked into the compressor 1, where the refrigerant is compressed into a high-temperature high-pressure state.
  • low temperature water obtained by cooling through the intermediate heat exchanger 5
  • the water, which has flowed into the heat exchanger 9 exchanges heat with indoor air, so that the water is heated. At this time, the indoor air is cooled.
  • the heated water passes through the valve 8b and then flows into the intermediate heat exchanger 5.
  • Fig. 3 is a diagram illustrating the flow of the refrigerant and that of the water during the heating operation in the air-conditioning apparatus 100 according to Embodiment 1.
  • solid line arrows indicate the flow of the refrigerant and broken line arrows indicate the flow of the water.
  • the four-way valve 2 is set so as to provide passages indicated by broken lines illustrated in Fig. 1 .
  • the opening degree of the valve 8a is set in such a manner that the flow rate of the water reaches a predetermined value.
  • the valve 8b is opened.
  • a high-temperature high-pressure refrigerant, obtained by the compressor 1, passes through the four-way valve 2 and flows into the intermediate heat exchanger 5.
  • the refrigerant which has flowed into the intermediate heat exchanger 5, exchanges heat with the water circulated through the water circuit 10, so that the refrigerant condenses into a liquid refrigerant.
  • the water circulated through the water circuit 10 is heated.
  • the liquid refrigerant passes through the expansion valve 4, where the refrigerant is expanded into a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the heat exchanger 3 and exchanges heat with the outdoor air, so that the refrigerant evaporates into a gas refrigerant.
  • the gas refrigerant passes through the four-way valve 2 and is sucked into the compressor 1 , where the refrigerant is compressed into a high-temperature high-pressure state.
  • the defrosting operation is performed when the heat exchanger 3 is covered with frost during the heating operation.
  • the operation during the defrosting operation is the same as that during the cooling operation.
  • the four-way valve 2 is set so as to provide the passages indicated by the solid lines illustrated in Fig. 1 .
  • the high-temperature high-pressure refrigerant obtained by the compressor 1 passes through the four-way valve 2 and then flows into the heat exchanger 3.
  • the frost on the heat exchanger 3 is melted by the high-temperature high-pressure refrigerant, which has flowed into the heat exchanger 3, and is then removed. Since the rest of the operation is the same as that during the cooling operation, description therefor is omitted.
  • the low temperature refrigerant flows into the intermediate heat exchanger 5.
  • the refrigerant at or below 0 degrees C may flow into the intermediate heat exchanger 5.
  • the water circulated through the water circuit 10 may freeze in the intermediate heat exchanger 5.
  • An increase in volume of water upon freezing may cause the intermediate heat exchanger 5 to be damaged.
  • a refrigerant passage in the intermediate heat exchanger 5 may communicate with a water passage therein, thus causing the refrigerant circulated through the refrigerant circuit 6 to leak into the water circuit 10.
  • the intermediate heat exchanger 5 may be damaged due to deterioration over time or the like, thus causing the refrigerant circulated through the refrigerant circuit 6 to leak into the water circuit 10.
  • a pressure in the water circuit 10 may exceed a withstanding pressure of, for example, pipes included in the water circuit 10 or welded part of the pipes, thus causing the water containing the refrigerant to leak into the room.
  • Fig. 4 is a flowchart illustrating an operation of the leakage detecting device 13 and that of the controller 14 in Embodiment 1.
  • the leakage detecting device 13 detects a pressure in the water circuit 10 at all times (S1: pressure detecting step) and determines whether the pressure in the water circuit 10 has increased (S2: increase determining step). When determining that the pressure has increased (YES in S2), the leakage detecting device 13 determines that the refrigerant has leaked into the water circuit 10 and transmits a detection signal indicating the leakage of the refrigerant to the controller 14 (S3: signal transmitting step). The controller 14 closes the valves 8a and 8b in response to reception of detection signal (S4: valve control step). Closing the valves 8a and 8b can prevent the water containing the refrigerant from flowing into the indoor unit 16.
  • the leakage detecting device 13 determines the increase of the pressure as follows.
  • a threshold value to be used during stop of the air-conditioning apparatus 100 is set to a pressure that is higher than the atmospheric pressure by a predetermined value.
  • the leakage detecting device 13 determines that the pressure has increased.
  • the pressure in the water circuit 10 is higher than that detected during stop of the air-conditioning apparatus 100 because the water is circulated.
  • the rate of the water circulated varies depending on, for example, the rotation speed of the pump 7, so that the pressure in the water circuit 10 also varies. Accordingly, a value that is higher than a maximum pressure, which may be measured so long as the refrigerant does not leak, in the water circuit 10 by a given value is determined as a threshold value in advance.
  • the leakage detecting device 13 determines that the pressure has increased.
  • the threshold values may be determined when the air-conditioning apparatus 100 is designed, for example.
  • operation simulation may be performed in consideration of actual conditions, such as the lengths of arranged pipes and the amount of refrigerant enclosed, and the threshold values may be determined on the basis of the simulation.
  • a threshold value may be determined in association with, for example, each of the rotation speed of the pump 7, an indoor air temperature, and an outdoor air temperature.
  • the leakage detecting device 13 may change a threshold value to be used depending on the rotation speed of the pump 7, the indoor air temperature, or the outdoor air temperature upon pressure detection.
  • a pressure increases in the entire water circuit 10 in principle. If the opening degree of the valve 8a is controlled in such a manner that the flow rate of the water circulated through the water circuit 10 is constant, however, the water containing a gas refrigerant is in a two-phase gas-liquid state. Accordingly, the difference between a pressure at a point prior to the valve 8a and a pressure at a point after the valve 8a may increase and a pressure at a point downstream of the valve 8a may be kept low, or increase very little.
  • the leakage detecting device 13 therefore detects a pressure at a point between the pump 7 and the valve 8a in the water circuit 10. Consequently, an increase in pressure can be reliably detected, irrespective of the opening degree of the valve 8a.
  • the air-conditioning apparatus 100 detects the leakage of the refrigerant circulated through the refrigerant circuit 6 into the water circuit 10 and closes the valves 8a and 8b.
  • the water containing the refrigerant can be prevented from flowing into the indoor unit 16. Consequently, the leakage of the refrigerant into the room can be prevented, thus preventing the room from being in an explosive atmosphere.
  • the controller 14 closes the valves 8a and 8b in response to reception of detection signal.
  • the controller 14 may close the valves 8a and 8b and stop the compressor 1 or the pump 7. Consequently, the leakage of the refrigerant can be prevented more reliably.
  • the controller 14 may prompt a user to ventilate the room upon receiving the detection signal.
  • the controller 14 may allow a remote control, which is used to enter an instruction for the indoor unit 16 or the air-conditioning apparatus 100, to output an audio message in order to prompt the user to ventilate the room.
  • the controller 14 may allow a display of the indoor unit 16 or the remote control to display a message in order to prompt the user to ventilate the room.
  • the leakage detecting device 13 detects a pressure in the water circuit 10 to detect the leakage of the refrigerant.
  • the leakage detecting device 13 may detect the leakage of the refrigerant by any other method.
  • the leakage detecting device 13 that detects the leakage of the refrigerant may be of, for example, a semiconductor type that utilizes a reduction in electrical resistance of a semiconductor caused by adsorption of a gas on the surface of the semiconductor, a contact burning type that utilizes an increase in electrical resistance of a platinum wire, through which current flows, caused by slight burning due to contact between the platinum wire and a gas, or a gas thermal conductivity type that utilizes a change in temperature of a platinum wire, through which current flows, (typically in contact with air) caused by contact between the platinum wire and a flammable gas because the thermal conductivity of the air differs from that of the gas.
  • a change in temperature of the platinum wire in the gas thermal conductivity type means a change in electrical resistance.
  • the above-described types use methods of detecting a flammable gas in a nonflammable gas (e.g., air).
  • An additional mechanism is therefore needed which allows the water circuit 10 to discharge a certain amount of water (or the mixture of the water and the refrigerant if the refrigerant has leaked) into the atmosphere at regular time intervals and detects the refrigerant using any of the above methods after removal of the water.
  • the certain amount of water may be discharged from the water circuit 10 into the atmosphere using a relief valve that is opened when the pressure is at or above the given pressure.
  • the relief valve may be disposed at the highest position in the water circuit 10 and the leakage of the refrigerant may be detected from the discharged mixture.
  • a low density flammable refrigerant tends to accumulate at the highest position in the water circuit 10. Accordingly, the leakage of the refrigerant can be reliably detected, irrespective of during operation or non-operation.
  • Embodiment 2 will be described with respect to an air-conditioning apparatus 100 including a plurality of primary circuits. Although the air-conditioning apparatus 100 including two primary circuits will be described below as an example, the air-conditioning apparatus 100 may include three or more primary circuits.
  • Fig. 5 is a diagram illustrating the configuration of the air-conditioning apparatus 100 according to Embodiment 2.
  • each blanked arrow indicates the flow of air and each dotted arrow indicates the flow of a signal.
  • the air-conditioning apparatus 100 includes a refrigerant circuit 6a (first refrigerant circuit or primary circuit) including a compressor 1a (first compressor), a four-way valve 2a, a heat exchanger 3a (first heat exchanger), an expansion valve 4a (first expansion mechanism), an intermediate heat exchanger 5a (first intermediate heat exchanger) sequentially connected in loop by pipes.
  • the air-conditioning apparatus 100 further includes a refrigerant circuit 6b (second refrigerant circuit or primary circuit) including a compressor 1b (second compressor), a four-way valve 2b, a heat exchanger 3b (second heat exchanger), an expansion valve 4b (second expansion mechanism), an intermediate heat exchanger 5b (second intermediate heat exchanger) sequentially connected in loop by pipes.
  • the air-conditioning apparatus 100 further includes a water circuit 10 (fluid circuit or secondary circuit) including the intermediate heat exchanger 5a, the intermediate heat exchanger 5b, a pump 7, a valve 8a (first valve), a heat exchanger 9 (load heat exchanger), and a valve 8b (second valve) sequentially connected in loop by pipes.
  • a flammable refrigerant such as a propane or isobutane, having a lower liquid density than water is circulated through each of the refrigerant circuits 6a and 6b, and water is circulated through the water circuit 10.
  • a fan 11 that delivers airflow to the heat exchangers 3a and 3b is disposed near the heat exchangers 3a and 3b.
  • a fan 12 that delivers airflow to the heat exchanger 9 is disposed near the heat exchanger 9.
  • the air-conditioning apparatus 100 further includes a leakage detecting device 13 that detects leakage of the refrigerant, circulated through the refrigerant circuits 6, into the water circuit 10 from any of the intermediate heat exchangers 5 and a controller 14 that closes the valves 8a and 8b when the leakage detecting device 13 detects the leakage of the refrigerant.
  • the compressors 1a and 1b, the four-way valves 2a and 2b, the heat exchangers 3a and 3b, the expansion valves 4a and 4b, the intermediate heat exchangers 5a and 5b, the pump 7, the valves 8a and 8b, the fan 11, the leakage detecting device 13, and the controller 14 of the components included in the air-conditioning apparatus 100 are accommodated in an outdoor unit 15 (first casing).
  • the heat exchanger 9 and the fan 12 of the components included in the air-conditioning apparatus 100 are accommodated in an indoor unit 16 (second casing).
  • Each of the intermediate heat exchangers 5a and 5b is a plate heat exchanger or double pipe heat exchanger that has high efficiency of heat exchange.
  • Fig. 6 is a diagram illustrating the flow of the refrigerant and that of the water during the cooling operation in the air-conditioning apparatus 100 according to Embodiment 2.
  • solid line arrows indicate the flow of the refrigerant and broken line arrows indicate the flow of the water.
  • the four-way valves 2a and 2b are set so as to provide passages indicated by solid lines illustrated in Fig. 5 .
  • An opening degree of the valve 8a is set in such a manner that the water flows at a constant rate.
  • the valve 8b is opened.
  • a high-temperature high-pressure refrigerant obtained by the compressor 1a, passes through the four-way valve 2a and flows into the heat exchanger 3a.
  • the refrigerant which has flowed into the heat exchanger 3a, exchanges heat with outdoor air, so that the refrigerant condenses into a liquid refrigerant.
  • the liquid refrigerant passes through the expansion valve 4a, where the refrigerant is expanded into a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the intermediate heat exchanger 5a and exchanges heat with the water circulated through the water circuit 10, so that the refrigerant evaporates into a gas refrigerant.
  • the water circulated through the water circuit 10 is cooled.
  • the gas refrigerant passes through the four-way valve 2a and is sucked into the compressor 1a, where the refrigerant is compressed into a high-temperature high-pressure state.
  • a high-temperature high-pressure refrigerant obtained by the compressor 1b, passes through the four-way valve 2b and flows into the heat exchanger 3b.
  • the refrigerant which has flowed into the heat exchanger 3b, exchanges heat with the outdoor air, so that the refrigerant condenses into a liquid refrigerant.
  • the liquid refrigerant passes through the expansion valve 4b, where the refrigerant is expanded into a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the intermediate heat exchanger 5b and exchanges heat with the water circulated through the water circuit 10, so that the refrigerant evaporates into a gas refrigerant. At this time, the water circulated through the water circuit 10 is cooled.
  • the gas refrigerant passes through the four-way valve 2b and is sucked into the compressor 1b, where the refrigerant is compressed into a high-temperature high-pressure state.
  • the water is cooled in the intermediate heat exchanger 5a and is further cooled to a low temperature in the intermediate heat exchanger 5b.
  • the low temperature water passes through the pump 7 and the valve 8a in sequence and then flows into the heat exchanger 9.
  • the water, which has flowed into the heat exchanger 9 exchanges heat with indoor air, so that the water is heated. At this time, the indoor air is cooled.
  • the heated water passes through the valve 8b and then flows into the intermediate heat exchanger 5a.
  • the water is successively cooled by the refrigerant circulated through the refrigerant circuit 6a and the refrigerant circulated through the refrigerant circuit 6b. Accordingly, the water can be adequately cooled if the capacity of each of the refrigerant circuits 6a and 6b is not high.
  • Fig. 7 is a diagram illustrating the flow of the refrigerant and that of the water during the heating operation in the air-conditioning apparatus 100 according to Embodiment 2.
  • solid line arrows indicate the flow of the refrigerant and broken line arrows indicate the flow of the water.
  • the four-way valves 2a and 2b are set so as to provide passages indicated by broken lines illustrated in Fig. 5 .
  • the opening degree of the valve 8a is set in such a manner that the flow rate of the water reaches a predetermined value.
  • the valve 8b is opened.
  • a high-temperature high-pressure refrigerant obtained by the compressor 1a, passes through the four-way valve 2a and flows into the intermediate heat exchanger 5a.
  • the refrigerant which has flowed into the intermediate heat exchanger 5a, exchanges heat with the water circulated through the water circuit 10, so that the refrigerant condenses into a liquid refrigerant.
  • the water circulated through the water circuit 10 is heated.
  • the liquid refrigerant passes through the expansion valve 4a, where the refrigerant is expanded into a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the heat exchanger 3a and exchanges heat with the outdoor air, so that the refrigerant evaporates into a gas refrigerant.
  • the gas refrigerant passes through the four-way valve 2a and is sucked into the compressor 1a, where the refrigerant is compressed into a high-temperature high-pressure state.
  • a high-temperature high-pressure refrigerant obtained by the compressor 1b, passes through the four-way valve 2b and flows into the intermediate heat exchanger 5b.
  • the refrigerant which has flowed into the intermediate heat exchanger 5b, exchanges heat with the water circulated through the water circuit 10, so that the refrigerant condenses into a liquid refrigerant.
  • the water circulated through the water circuit 10 is heated.
  • the liquid refrigerant passes through the expansion valve 4b, where the refrigerant is expanded into a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the heat exchanger 3b and exchanges heat with the outdoor air, so that the refrigerant evaporates into a gas refrigerant.
  • the gas refrigerant passes through the four-way valve 2b and is sucked into the compressor 1b, where the refrigerant is compressed into a high-temperature high-pressure state.
  • the water is heated in the intermediate heat exchanger 5a and is further heated to a high temperature in the intermediate heat exchanger 5b.
  • the high temperature water passes through the pump 7 and the valve 8a in sequence and then flows into the heat exchanger 9.
  • the water, which has flowed into the heat exchanger 9 exchanges heat with the indoor air, so that the water is cooled. At this time, the indoor air is heated.
  • the cooled water passes through the valve 8b and then flows into the intermediate heat exchanger 5a.
  • the water is successively heated by the refrigerant circulated through the refrigerant circuit 6a and the refrigerant circulated through the refrigerant circuit 6b. Accordingly, the water can be adequately heated if the capacity of each of the refrigerant circuits 6a and 6b is not high.
  • the defrosting operation is performed when the heat exchangers 3a and 3b are covered with frost during the heating operation.
  • the four-way valves 2a and 2b are set so as to provide the passages indicated by the solid lines illustrated in Fig. 5 .
  • the high-temperature high-pressure refrigerant, obtained by the compressor 1a passes through the four-way valve 2a and flows into the heat exchanger 3a.
  • the high-temperature high-pressure refrigerant, obtained by the compressor 1b passes through the four-way valve 2b and flows into the heat exchanger 3b.
  • the frost on the heat exchangers 3a and 3b is melted by the high-temperature high-pressure refrigerant which has flowed into the heat exchangers 3a and 3b and is then removed. Since the rest of the operation is the same as that during the cooling operation, description is omitted.
  • the intermediate heat exchangers 5a and 5b may be damaged and the refrigerant circulated through the refrigerant circuits 6 may leak into the water circuit 10. If the refrigerant leaks into the water circuit 10, the water containing the refrigerant may leak into a room.
  • the controller 14 closes the valves 8a and 8b. This prevents the leakage of the water containing the refrigerant from flowing into the indoor unit 16.
  • the controller 14 may stop the compressors 1a and 1b or the pump 7 to reliably prevent the leakage of the refrigerant.
  • the air-conditioning apparatus 100 according to Embodiment 2 detects the leakage of the refrigerant circulated through the refrigerant circuits 6a and 6b into the water circuit 10 and closes the valves 8a and 8b.
  • the water containing the refrigerant can be prevented from flowing into the indoor unit 16. Consequently, the leakage of the refrigerant into the room can be prevented, thus preventing the room from being in an explosive atmosphere.
  • the amount of refrigerant enclosed in each primary circuit be below a predetermined amount (for example, 150 g, based on the F-gas Regulation in Europe, in the use of propane as a refrigerant, for example) so that a room is prevented from being in an explosive atmosphere if the refrigerant leaks into the room.
  • a predetermined amount for example, 150 g, based on the F-gas Regulation in Europe, in the use of propane as a refrigerant, for example
  • a large amount of refrigerant is enclosed in a large air-conditioning apparatus having a high capacity.
  • the air-conditioning apparatus 100 including the two primary circuits, namely, the refrigerant circuits 6a and 6b, if the refrigerant enclosed in each of the refrigerant circuits 6a and 6b is restricted to a small amount and the capacity of each of the refrigerant circuits 6a and 6b is accordingly low, the air-conditioning apparatus 100 can demonstrate a high capacity. In other words, if the air-conditioning apparatus 100 according to Embodiment 2 is a large air-conditioning apparatus that demonstrates a high capacity, the amount of refrigerant enclosed in each primary circuit can be small.
  • the airflow delivered by the fan 11 passes through the heat exchanger 3a and then passes through the heat exchanger 3b.
  • the heat exchanger 3a exchanges heat between the air and the refrigerant circulated through the refrigerant circuit 6a and the heated air is delivered to the heat exchanger 3b.
  • the temperature of the airflow supplied to the heat exchanger 3a differs from that of the airflow supplied to the heat exchanger 3b. Consequently, a condensing temperature in the refrigerant circuit 6a can be allowed to differ from that in the refrigerant circuit 6b.
  • the water circulated through the water circuit 10 passes through the intermediate heat exchanger 5a and then passes through the intermediate heat exchanger 5b.
  • the intermediate heat exchanger 5a exchanges heat between the water and the refrigerant circulated through the refrigerant circuit 6a and the cooled water is delivered to the intermediate heat exchanger 5b.
  • the temperature of the water supplied to the intermediate heat exchanger 5a differs from that of the water supplied to the intermediate heat exchanger 5b. Consequently, an evaporating temperature in the refrigerant circuit 6a can be allowed to differ from that in the refrigerant circuit 6b.
  • the condensing temperature and the evaporating temperature in the refrigerant circuit 6a can be allowed to differ from those in the refrigerant circuit 6b.
  • the condensing temperature and the evaporating temperature in the refrigerant circuit 6a during the heating operation can similarly be allowed to differ from those in the refrigerant circuit 6b. Since the condensing temperature and the evaporating temperature in the refrigerant circuit 6a are allowed to differ from those in the refrigerant circuit 6b, the temperature of the refrigerant is allowed to change depending on the temperature of water or air, thus enabling the air-conditioning apparatus to achieve high efficiency.
  • the air heated by heat exchange through the heat exchanger 3a is delivered to the heat exchanger 3b, so that the condensing temperature in the heat exchanger 3a is low and the condensing temperature in the heat exchanger 3b is high.
  • the water cooled by heat exchange through the intermediate heat exchanger 5a flows into the intermediate heat exchanger 5b, so that the evaporating temperature in the intermediate heat exchanger 5a is high and the evaporating temperature in the intermediate heat exchanger 5b is low.
  • the air cooled by heat exchange through the heat exchanger 3a is delivered to the heat exchanger 3b, so that the evaporating temperature in the heat exchanger 3a is high and the evaporating temperature in the heat exchanger 3b is low.
  • the water heated by heat exchange through the intermediate heat exchanger 5a flows into the intermediate heat exchanger 5b, so that the condensing temperature in the intermediate heat exchanger 5a is low and the condensing temperature in the intermediate heat exchanger 5b is high.
  • the refrigerant circuit 6a is a circuit in which the condensing temperature is low and the evaporating temperature is high and the refrigerant circuit 6b is a circuit in which the condensing temperature is high and the evaporating temperature is low. Accordingly, the difference between a high pressure and a low pressure is reduced in the refrigerant circuit 6a and the difference therebetween is increased in the refrigerant circuit 6b.
  • the difference in high-low pressure difference between the refrigerant circuit 6a and the refrigerant circuit 6b may be reduced by allowing the airflow generated by the fan 11 to pass through the heat exchanger 3b and then pass through the heat exchanger 3a, or allowing the water circulated through the water circuit 10 to pass through the intermediate heat exchanger 5b and then pass through the intermediate heat exchanger 5a.
  • the increase or the decrease may be selected depending on the difference in performance between the compressors included in the refrigerant circuits 6a and 6b, an installation environment of the air-conditioning apparatus 100, or the like so that high efficiency is achieved.
  • Embodiment 3 will be described with respect to placement of the intermediate heat exchanger 5 (5a, 5b) in Embodiments 1 and 2. The placement will be described with respect to the air-conditioning apparatus 100 according to Embodiment 2 as an example.
  • Fig. 8 is an exploded perspective view of a typical plate heat exchanger.
  • Figs. 9 to 11 are diagrams illustrating arrangement of the intermediate heat exchangers 5a and 5b according to Embodiment 3.
  • solid line arrows indicate the flow of refrigerant during the cooling operation and broken line arrows indicate the flow of water.
  • the refrigerant flows in a direction opposite to that indicated by the solid line arrows.
  • an up-down direction corresponds to a vertical direction.
  • each of the intermediate heat exchangers 5a and 5b is a plate heat exchanger.
  • the plate heat exchanger includes a plurality of substantially rectangular plates 51 arranged and has a thin rectangular-parallelepiped shape in appearance.
  • the plate 51 at one end of the stacked plates 51 has connection ports 52 and 53 for the primary circuit and connection ports 54 and 55 for the secondary circuit.
  • Refrigerant passages 56 through which the refrigerant circulated through the primary circuit flows and water passages 57 through which the water circulated through the secondary circuit flows are alternately arranged between the adjacent plates.
  • the two rectangular-parallelepiped intermediate heat exchangers 5a and 5b are vertically stacked.
  • the outdoor unit 15 is increased in size and the area of installation of the outdoor unit 15 is also increased. Since the two intermediate heat exchangers 5a and 5b are vertically stacked as illustrated in Fig. 9 , however, the intermediate heat exchangers 5a and 5b can be arranged with efficiency. Thus, the installation area of the outdoor unit 15 can be reduced.
  • connection ports 53a and 53b adjacent to the expansion valves 4a and 4b and connection ports 55a and 55b adjacent to the pump 7 are arranged on a lower side and connection ports 52a and 52b adjacent to the four-way valves 2a and 2b and connection ports 54a and 54b adjacent to the valve 8b are arranged on an upper side.
  • the two-phase refrigerant enters through the connection ports 53a and 53b and the gas refrigerant leaves through the connection ports 52a and 52b.
  • the gas refrigerant enters through the connection ports 52a and 52b and the liquid refrigerant leaves through the connection ports 53a and 53b.
  • the connection ports 52a and 52b through which the gas refrigerant passes are arranged on the upper side, therefore, accumulation of the gas refrigerant in the intermediate heat exchangers 5a and 5b can be prevented.
  • the intermediate heat exchangers 5a and 5b are inclined in such a manner that the connection ports 52a, 52b, 54a, and 54b face obliquely upward.
  • the area of installation of the outdoor unit 15 is slightly increased, the area of accumulation of the gas refrigerant in an upper portion (area 58a or 58b indicated by a broken line in Fig. 9 ) of each of the intermediate heat exchangers 5a and 5b can be reduced.
  • connection ports 52a, 52b, 54a, and 54b are arranged at one ends and the connection ports 53a, 53b, 55a, and 55b are provided in the plates 51 arranged at the another ends, respectively.
  • the connection ports 53a and 53b are inlets for the refrigerant during the cooling operation and the defrosting operation.
  • the refrigerant gas may accumulate in the intermediate heat exchangers 5a and 5b and detection of the leakage of the refrigerant may accordingly be delayed.
  • the above-described arrangement manner can reduce the areas where the refrigerant gas accumulates in the intermediate heat exchangers 5a and 5b. Consequently, the leakage of the refrigerant can be immediately detected.
  • the intermediate heat exchangers 5a and 5b in Embodiment 2 have been described above as an example.
  • the intermediate heat exchanger 5 may be placed vertically as illustrated in Fig. 9 .
  • the intermediate heat exchanger 5 may be inclined as illustrated in Fig. 10 .
  • the connection ports may be provided in the plates 51 arranged at the another ends as illustrated in Fig. 11 .
  • each intermediate heat exchanger is vertically placed and the intermediate heat exchangers are arranged side by side horizontally.
  • the intermediate heat exchangers 5a and 5b are arranged side by side horizontally in a state in which the connection ports 53a, 53b, 55a, and 55b are arranged on the lower side and the connection ports 52a, 52b, 54a, and 54b are arranged on the upper side. Consequently, the performance can be ensured and an upper space within the outdoor unit 15 can be used as a refrigerant pipe space, so that the area of installation can be reduced.
  • the water is circulated through the water circuit 10 which serves as the secondary circuit.
  • the fluid circulated through the secondary circuit is not limited to water. Any other nonflammable fluid, such as brine, may be used.
  • Embodiments 1 and 2 are effective in the case where brine is circulated through the secondary circuit.
  • the pump 7 is disposed between the intermediate heat exchanger 5 (the intermediate heat exchanger 5b in Embodiment 2) and the valve 8a in the water circuit 10.
  • the pump 7 may be disposed at any other position between the valves 8a and 8b in a direction in which the water is circulated.
  • the leakage detecting device 13 can detect a pressure at a point between the pump 7 and the valve 8a in the water circuit 10 to reliably detect the leakage of the refrigerant, irrespective of the position of the pump 7.
  • Embodiments 1 and 2 have been described with respect to the air-conditioning apparatus as an example of the heat pump apparatus.
  • the air-conditioning apparatus is not limited to a room air-conditioning apparatus in which the amount of refrigerant is relatively small and may include a large air-conditioning apparatus, such as a package air-conditioning apparatus for business use or a multi-air-conditioning apparatus for a building.
  • the heat pump apparatus is not limited to an air-conditioning apparatus and may be, for example, a chiller or a cooler. In this case, instead of water, brine has to be used as a fluid for the secondary circuit. Furthermore, the four-way valve is not needed because the apparatus is used only for refrigeration or cooling in this case.

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Claims (11)

  1. Wärmepumpenvorrichtung, umfassend:
    einen ersten Kältemittelkreislauf (6), durch den ein Kältemittel zirkuliert wird, wobei der Kältemittelkreislauf (6) einen ersten Verdichter (1), einen ersten Wärmequellenwärmetauscher (3a), einen ersten Expansionsmechanismus (4) und einen ersten Zwischenwärmetauscher (5) beinhaltet, die nacheinander in Schleife über Leitungen verbunden sind;
    einen Fluidkreislauf (10), durch den ein Fluid zirkuliert wird, wobei der Fluidkreislauf (10) den ersten Zwischenwärmetauscher (5), eine Pumpe (7), ein erstes Ventil (8a), einen Lastwärmetauscher (9) und ein zweites Ventil (8b) beinhaltet, die nacheinander in Schleife über Leitungen verbunden sind; und
    eine Leckageerfassungseinrichtung (13), die Leckage des Kältemittels erfasst, das durch den ersten Kältemittelkreislauf (6) vom ersten Zwischenwärmetauscher (5) in den Fluidkreislauf (10) zirkuliert wird, dadurch gekennzeichnet, dass
    die Wärmepumpenvorrichtung ferner eine Steuerung (14) umfasst, die einen Öffnungsgrad des ersten Ventils (8a) in einer solchen Weise steuert, dass das durch den Fluidkreislauf (10) zirkulierte Fluid mit einer vorgegebenen Durchflussrate strömt und das erste Ventil (8a) und das zweite Ventil (8b), die im Fluidkreislauf (10) enthalten sind, schließt, wenn die Leckageerfassungseinrichtung (13) die Kältemittelleckage erfasst,
    wobei die Pumpe (7) das Fluid in einer solchen Weise zirkuliert, dass das Fluid den ersten Zwischenwärmetauscher (5), das erste Ventil (8a), den Lastwärmetauscher (9) und das zweite Ventil (8b) in dieser Reihenfolge durchströmt, und
    wobei die Leckageerfassungseinrichtung (13) zwischen der Pumpe (7) und dem ersten Ventil (8a) im Fluidkreislauf (10) platziert ist und die Kältemittelleckage durch Erfassen eines Drucks im Fluidkreislauf (10) erfasst.
  2. Wärmepumpenvorrichtung nach Anspruch 1, ferner umfassend:
    ein erstes Gehäuse (15), das den ersten Verdichter (1), den ersten Wärmequellenwärmetauscher (3a), den ersten Expansionsmechanismus (4), den ersten Zwischenwärmetauscher (5), das erste Ventil (8a) und das zweite Ventil (8b) beherbergt; und
    ein zweites Gehäuse (16), das den Lastwärmetauscher (9) beherbergt.
  3. Wärmepumpenvorrichtung nach Anspruch 1 oder 2,
    wobei das durch den ersten Kältemittelkreislauf (6) zirkulierte Kältemittel entzündlich ist, und
    wobei das durch den Fluidkreislauf (10) zirkulierte Fluid nicht entzündlich ist.
  4. Wärmepumpenvorrichtung nach einem der Ansprüche 1 bis 3, wobei die Steuerung (14) den ersten Verdichter (1) anhält, wenn die Leckageerfassungseinrichtung (13) die Kältemittelleckage erfasst.
  5. Wärmepumpenvorrichtung nach einem der Ansprüche 1 bis 4, wobei der erste Zwischenwärmetauscher (5) in einer solchen Weise platziert ist, dass ein Verbindungsanschluss für die mit dem ersten Verdichter (1) verbundene Leitung in einem oberen Teil des ersten Zwischenwärmetauschers (5) bereitgestellt ist und ein Verbindungsanschluss für die mit dem ersten Expansionsmechanismus (4) verbundene Leitung in einem unteren Teil desselben bereitgestellt ist.
  6. Wärmepumpenvorrichtung nach Anspruch 5,
    wobei der erste Zwischenwärmetauscher (5) ein Plattenwärmetauscher ist, der eine Vielzahl von übereinander gestapelten Platten (51) beinhaltet und eine Platte an einem Ende der gestapelten Platten (51) den Verbindungsanschluss für die mit dem ersten Verdichter (1) verbundene Leitung und den Verbindungsanschluss für die mit dem ersten Expansionsmechanismus (4) verbundene Leitung aufweist, und
    wobei der erste Zwischenwärmetauscher (5) in einer solchen Weise geneigt ist, dass der Verbindungsanschluss für die mit dem ersten Verdichter (1) verbundene Leitung schräg nach oben zeigt.
  7. Wärmepumpenvorrichtung nach Anspruch 6,
    wobei der erste Zwischenwärmetauscher (5) ein Plattenwärmetauscher ist, in dem der Verbindungsanschluss für die mit dem ersten Verdichter (1) verbundene Leitung in einer Platte an einem Ende der Vielzahl von Platten (51) angeordnet ist, das ein anderes Ende ist als das, an dem die Platte (51) mit dem Verbindungsanschluss für die mit dem ersten Expansionsmechanismus (4) verbundene Leitung angeordnet ist, und
    wobei der erste Zwischenwärmetauscher (5) in einer solchen Weise geneigt ist, dass der Verbindungsanschluss für die mit dem ersten Verdichter (1) verbundene Leitung schräg nach oben zeigt und der Verbindungsanschluss für die mit dem ersten Expansionsmechanismus (4) verbundene Leitung schräg nach unten zeigt.
  8. Wärmepumpenvorrichtung nach einem der Ansprüche 1 bis 7, ferner umfassend:
    einen zweiten Kältemittelkreislauf (6b), durch den das Kältemittel zirkuliert wird, wobei der zweite Kältemittelkreislauf (6b) einen zweiten Verdichter (1b), einen zweiten Wärmequellenwärmetauscher (3b), einen zweiten Expansionsmechanismus (4b) und einen zweiten Zwischenwärmetauscher (5b) beinhaltet, die nacheinander in Schleife über Leitungen verbunden sind;
    wobei der zweite Zwischenwärmetauscher (5b) zwischen dem ersten Zwischenwärmetauscher (5) und dem ersten Ventil (8a) im Fluidkreislauf (10) angebunden ist,
    wobei die Leckageerfassungseinrichtung (13) die Leckage des Kältemittels, das durch den ersten Kältemittelkreislauf (6) zirkuliert wird und des Kältemittels, das durch den zweiten Kältemittelkreislauf (6b) vom ersten Zwischenwärmetauscher (5) in den Fluidkreislauf (10) zirkuliert wird, erfasst.
  9. Wärmepumpenvorrichtung nach Anspruch 8 in Abhängigkeit von einem der Ansprüche 1 bis 4,
    wobei das durch die ersten (6) und zweiten (6b) Kältemittelkreisläufe zirkulierte Kältemittel R32 oder eine Kältemittelmischung mit R32 ist,
    wobei jeder der ersten (5) und zweiten (5b) Zwischenwärmetauscher ein Plattenwärmetauscher mit einer Vielzahl von übereinander gestapelten Platten (51) ist, und
    wobei jeder der ersten (5) und zweiten (5b) Zwischenwärmetauscher in einer solchen Weise platziert ist, dass die Verbindungsanschlüsse für die Leitungen auf einer Oberseite und einer Unterseite in einer vertikalen Richtung positioniert sind und die ersten (5) und zweiten (5b) Zwischenwärmetauscher horizontal nebeneinander angeordnet sind.
  10. Wärmepumpenvorrichtung nach Anspruch 8 oder 9, ferner umfassend:
    einen Lüfter (11), der einen Luftstrom erzeugt, um Luft, die mit dem Kältemittel in einem der ersten (3a) und zweiten (3b) Wärmequellenwärmetauscher Wärme ausgetauscht hat, zu dem anderen der ersten (3a) und zweiten (3b) Wärmequellenwärmetauscher zu liefern und der gelieferten Luft zu ermöglichen, Wärme mit dem Kältemittel in dem anderen Wärmequellenwärmetauscher auszutauschen.
  11. Wärmepumpenvorrichtung nach Anspruch 2,
    wobei die Wärmepumpenvorrichtung eine Klimaanlage (100) ist, die Luft in einem Raum klimatisiert,
    wobei das erste Gehäuse (15) eine Außeneinheit (15) ist, die außerhalb des Raumes eingerichtet ist, und
    wobei das zweite Gehäuse (16) eine Inneneinheit ist, die innerhalb des Raumes eingerichtet ist.
EP12832013.2A 2011-09-13 2012-01-31 Wärmepumpenvorrichtung Active EP2759787B1 (de)

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EP2759787A1 (de) 2014-07-30
CN103797317A (zh) 2014-05-14
WO2013038577A1 (ja) 2013-03-21
JPWO2013038577A1 (ja) 2015-03-23
US20140196483A1 (en) 2014-07-17
CN103797317B (zh) 2016-08-17
JP5818900B2 (ja) 2015-11-18

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