EP2960602B1 - Klimaanlage - Google Patents

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Publication number
EP2960602B1
EP2960602B1 EP13875678.8A EP13875678A EP2960602B1 EP 2960602 B1 EP2960602 B1 EP 2960602B1 EP 13875678 A EP13875678 A EP 13875678A EP 2960602 B1 EP2960602 B1 EP 2960602B1
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EP
European Patent Office
Prior art keywords
heat
refrigerant
heat medium
operation mode
air
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.)
Active
Application number
EP13875678.8A
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English (en)
French (fr)
Other versions
EP2960602A1 (de
EP2960602A4 (de
Inventor
Yuji Motomura
Daisuke Shimamoto
Takayoshi Honda
Osamu Morimoto
Koji Nishioka
Tatsuo Ono
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
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Mitsubishi Electric Corp
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Publication of EP2960602A1 publication Critical patent/EP2960602A1/de
Publication of EP2960602A4 publication Critical patent/EP2960602A4/de
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    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F24F3/065—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units with a plurality of evaporators or 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0312—Pressure sensors near the indoor heat exchanger
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present invention relates to an air-conditioning apparatus applied to, for example, a multi-air-conditioning apparatus for buildings.
  • a conventional air-conditioning apparatus such as a multi-air-conditioning apparatus for buildings, for example, causes refrigerant to circulate between an outdoor unit, which is a heat source unit arranged outside a structure, and an indoor unit arranged inside the structure.
  • the refrigerant transfers or receives heat, and the heated or cooled air causes air-conditioning target space to be cooled or heated.
  • a refrigerant used for such an air-conditioning apparatus for example, an HFC (hydro-fluorocarbon) refrigerant is often used.
  • a natural refrigerant such as carbon dioxide (CO 2 ) has also been proposed.
  • CO 2 535 652 A1 discloses an air-conditioning apparatus having the features according to the preamble of claim 1.
  • a heat source unit arranged outside a structure generates cooling energy or heating energy.
  • a heat exchanger arranged inside the heat source unit heats or cools water, antifreeze, or the like, and the heated or cooled water, antifreeze, or the like is conveyed to a fan coil unit, a panel heater, or the like, which is an indoor unit, thereby performing cooling or heating (see, for example, Patent Literature 1).
  • An apparatus called an exhaust heat recovery-type chiller has also been available in which four water pipes are connected between a heat source unit and an indoor unit, cooled or heated water or the like is simultaneously supplied, and cooling or heating can be freely selected in the indoor unit (see, for example, Patent Literature 2).
  • An apparatus has also been available which is configured such that heat exchangers for a primary refrigerant and a secondary refrigerant are arranged in the vicinity of each indoor unit and the secondary refrigerant is conveyed to the indoor unit (see, for example, Patent Literature 3).
  • an apparatus which is configured such that an outdoor unit and a branch unit that includes a heat exchanger are connected by two pipes and a secondary refrigerant is conveyed to an indoor unit (see, for example, Patent Literature 4).
  • an air-conditioning apparatus such as a multi-air-conditioning apparatus for buildings has also been available which is configured such that by causing refrigerant to circulate from an outdoor unit to a relay unit and causing a heat medium such as water to circulate from the relay unit to an indoor unit, the heat medium such as water may be caused to circulate to the indoor unit (see, for example, Patent Literature 5).
  • the air-conditioning apparatus described in Patent Literature 4 has a configuration which is wasteful in terms of energy since a primary refrigerant after being subjected to heat exchange flows into the same flow passage as that for a primary refrigerant before being subjected to heat exchange and each of a plurality of indoor units thus cannot exhibit the maximum performance when the plurality of indoor units are connected. Furthermore, the configuration in which the connection between a branch unit and an extension pipe is achieved using four pipes in total, that is, two pipes for cooling and two pipes for heating, is consequently similar to the configuration of the system in which an outdoor unit and a branch unit are connected by four pipes, thereby degrading the workability.
  • EP 2 535 652 A1 discloses an air-conditioning apparatus comprising a heating operation mode that heats a heat medium in at least one of the heat exchangers related to heat medium, a heat recovery defrosting operation mode that melts frost attached to a heat source side heat exchanger during the heating operation mode by operating at least one of the pumps and by making a heat source side refrigerant received heat from the heat medium that is flowing in the at least one of the heat exchangers related to heat medium, and a bypass defrosting operation mode that melts frost attached to the heat source side heat exchanger during the heating operation mode by passing a portion or all of the heat source side refrigerant through a bypass piping.
  • WO 2013/008365 A1 describes a similar air-conditioning apparatus wherein a refrigerant flow path switching device is switched to execute a defrost operation mode in which a refrigerant discharged from the compressor is supplied to the heat-source-side heat exchanger.
  • a defrost operation mode part of a refrigerant flowing out from the heat-source-side heat exchanger is supplied to intermediate heat exchanger without passing through an expansion device, and the rest of the refrigerant is returned to the outdoor unit without passing through the expansion device and the intermediate heat exchanger.
  • the present invention has been made to solve the above problem, and an object of the present invention is to provide an air-conditioning apparatus that has a plurality of defrosting operation modes to achieve maintenance of comfort.
  • An air-conditioning apparatus is defined by the features of claim 1. Preferred embodiments of this apparatus are represented in the dependent claims.
  • An air-conditioning apparatus has, as a defrosting operation mode, a "heat recovery defrosting operation mode” and a "bypass defrosting operation mode". Therefore, either one of the defrosting operation modes may be executed, and maintenance of comfort may thus be achieved.
  • Fig. 1 is a schematic diagram illustrating an exemplary installation of an air-conditioning apparatus according to Embodiment of the present invention.
  • An exemplary installation of an air-conditioning apparatus will be explained with reference to Fig. 1 .
  • a refrigeration cycle a refrigerant circulation circuit A, a heat medium circulation circuit B
  • refrigerant a heat-source-side refrigerant, a heat medium
  • each indoor unit can freely select, as an operation mode, a cooling mode or a heating mode.
  • Fig. 1 schematically illustrates the overall configuration of an air-conditioning apparatus including a plurality of indoor units 3 connected.
  • the size relationship of individual component members may differ from the actual size relationship.
  • the air-conditioning apparatus includes an outdoor unit (heat source unit) 1, a plurality of indoor units 3, and a relay unit 2 which is arranged between the outdoor unit 1 and the indoor units 3.
  • the relay unit 2 exchanges heat between a heat-source-side refrigerant and a heat medium.
  • the outdoor unit 1 and the relay unit 2 are connected by refrigerant pipes 4 through which the heat-source-side refrigerant flows.
  • the relay unit 2 and the indoor units 3 are connected by pipes (heat medium conveyance pipes) 5 through which the heat medium flows. Cooling energy or heating energy generated at the outdoor unit 1 is delivered to the indoor units 3 via the relay unit 2.
  • the outdoor unit 1 is normally placed in an outdoor space 6, which is a space (for example, a rooftop etc.) outside a structure 9 such as a building, and supplies cooling energy or heating energy to the indoor units 3 via the relay unit 2.
  • the indoor units 3 are placed at positions from which cooling air or heating air may be supplied to an indoor space 7, which is a space (for example, a living room etc.) inside the structure 9, and supplies the cooling air or the heating air to the indoor space 7 serving as an air-conditioning target space.
  • the relay unit 2 is configured to be installed at a position which is different from the outdoor space 6 and the indoor space 7 as a housing which is different from the outdoor unit 1 and the indoor units 3.
  • the relay unit 2 is connected to the outdoor unit 1 and the indoor units 3 by the refrigerant pipes 4 and the pipes 5, respectively, and transmits to the indoor units 3 the cooling energy or heating energy supplied from the outdoor unit 1.
  • a heat-source-side refrigerant is conveyed from the outdoor unit 1 to the relay unit 2 via the refrigerant pipes 4.
  • the conveyed heat-source-side refrigerant exchanges heat with a heat medium at an intermediate heat exchanger (an intermediate heat exchanger 25 described later) inside the relay unit 2 to heat or cool the heat medium. That is, hot water or cold water is generated at the intermediate heat exchanger.
  • the hot water or the cold water generated at the relay unit 2 is conveyed by a heat medium conveyance device (a pump 31 described later) to the indoor units 3 via the pipes 5, and is used at the indoor units 3 for a heating operation (may be an operation state requiring hot water) or a cooling operation (may be an operation state requiring cold water) for the indoor space 7.
  • a single-component refrigerant such as R-22, R-134a, or R-32
  • a near-azeotropic refrigerant mixture such as R-410A or R-404A
  • a non-azeotropic refrigerant mixture such as R-407C
  • heat medium for example, water, antifreeze, a liquid mixture of antifreeze and water, a liquid mixture of water and an additive having high anti-corrosion effect, or the like may be used.
  • the outdoor unit 1 and the relay unit 2 are connected by the two refrigerant pipes 4, and the relay unit 2 and each of the indoor units 3 are connected by the two pipes 5.
  • the relay unit 2 and each of the indoor units 3 are connected by the two pipes 5.
  • a state is illustrated as an example in which the relay unit 2 is installed in a space (hereinafter, simply referred to as a space 8) such as a space above a ceiling, which is a space that is within the structure 9 but is different from the indoor space 7. Therefore, the relay unit 2 may be installed in any place other than the space above the ceiling as long as it is a space ventilated to the outside to some extent and is not a living space.
  • the relay unit 2 may be installed in a space which is ventilated to the outside, such as a common space in which an elevator or the like is located, or the like.
  • the relay unit 2 may be installed at a position near the outdoor unit 1. However, when the distance from the relay unit 2 to the indoor units 3 is too long, the heat medium conveyance force is significantly large. Therefore, it should be noted that an energy saving effect is reduced.
  • the outdoor unit 1 is installed in the outdoor space 6 as an example.
  • the outdoor unit 1 is not necessarily installed as described above.
  • the outdoor unit 1 may be installed in an enclosed space, such as a machine room with a ventilation opening.
  • the outdoor unit 1 may be installed inside the structure 9 as long as waste heat can be exhausted outside the structure 9 via an exhaust duct.
  • an outdoor unit 1 of a water-cooled type may be installed inside the structure 9. When the outdoor unit 1 is installed in such a place, there will be no particular problem.
  • the indoor units 3 are of a ceiling cassette type is illustrated as an example.
  • the indoor units 3 are not necessarily of the above type.
  • the indoor units 3 may be of any type such as a ceiling concealed type or ceiling suspended type as long as they are able to blow heating air or cooling air to the indoor space 7 directly or through a duct or the like.
  • the number of connected outdoor units 1, indoor units 3, and relay units 2 is not limited to that illustrated in Fig. 1 .
  • the number of connected outdoor units 1, indoor units 3, and relay units 2 may be determined in accordance with the structure 9 in which the air-conditioning apparatus according to Embodiment is installed.
  • the plurality of relay units 2 may be installed in different positions in a common space in a structure such as a building or a space such as a space above a ceiling.
  • a structure such as a building or a space such as a space above a ceiling.
  • an intermediate heat exchanger inside each of the relay units 2 is able to cover an air-conditioning load.
  • the indoor units 3 may be installed at a distance or a height within an allowable conveyance range of the heat medium conveyance device in the individual relay units 2, and an arrangement for the entire structure such as a building can be attained.
  • Fig. 2 is a schematic circuit configuration diagram illustrating an example of a circuit configuration of the air-conditioning apparatus (hereinafter, referred to as an air-conditioning apparatus 100) according to Embodiment of the present invention.
  • the configuration of the air-conditioning apparatus 100 that is, the workings of individual actuators forming a refrigerant circuit, will be explained in detail with reference to Fig. 2 .
  • the outdoor unit 1 and the relay unit 2 are connected by the refrigerant pipes 4 via an intermediate heat exchanger (refrigerant-water heat exchanger) 25a and an intermediate heat exchanger (refrigerant-water heat exchanger) 25b which are provided in the relay unit 2.
  • the relay unit 2 and the indoor units 3 are connected by the pipes 5 via the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • a compressor 10 In the outdoor unit 1, a compressor 10, a first refrigerant flow switching device 11 such as a four-way valve, a heat-source-side heat exchanger 12, and an accumulator 19 are provided by being connected in series by the refrigerant pipes 4.
  • the outdoor unit 1 also includes a refrigerant connection pipe 4a, a refrigerant connection pipe 4b, a check valve 13a, a check valve 13b, a check valve 13c, and a check valve 13d.
  • the flow of a heat-source-side refrigerant which is to be caused to flow into the relay unit 2 may be fixed to a certain direction, irrespective of the operation required by the indoor units 3.
  • the compressor 10 sucks a heat-source-side refrigerant, compresses the heat-source-side refrigerant into a high-temperature and high-pressure state, and conveys the heat-source-side refrigerant to the refrigerant circulation circuit A.
  • the compressor 10 may be, for example, an inverter compressor whose capacity can be controlled.
  • the first refrigerant flow switching device 11 switches between providing the flow of a heat-source-side refrigerant in a heating operation mode (in a heating only operation mode and a heating main operation mode) and providing the flow of a heat-source-side refrigerant in cooling operation mode (in a cooling only operation mode and a cooling main operation mode).
  • the heat-source-side heat exchanger 12 serves as an evaporator during a heating operation and serves as a condenser (or a radiator) during a cooling operation.
  • the heat-source-side heat exchanger 12 exchanges heat between fluid such as air supplied from a blower device such as a fan, which is not illustrated in the drawing, and a heat-source-side refrigerant to evaporate and gasify or condense and liquefy the heat-source-side refrigerant.
  • the accumulator 19 is provided on the suction side of the compressor 10, and stores excess refrigerant caused by a difference between the heating operation time and the cooling operation time or excess refrigerant with respect to a transient change in the operation.
  • the check valve 13c is provided at a position of the refrigerant pipe 4 between the relay unit 2 and the first refrigerant flow switching device 11, and allows a heat-source-side refrigerant to flow only in a specific direction (direction from the relay unit 2 to the outdoor unit 1).
  • the check valve 13a is provided at a position of the refrigerant pipe 4 between the heat-source-side heat exchanger 12 and the relay unit 2, and allows a heat-source-side refrigerant to flow only in a specific direction (direction from the outdoor unit 1 to the relay unit 2).
  • the check valve 13d is provided at the refrigerant connection pipe 4a, and causes the heat-source-side refrigerant discharged from the compressor 10 to flow to the relay unit 2 during a heating operation.
  • the check valve 13b is provided at the refrigerant connection pipe 4b, and causes the heat-source-side refrigerant returned from the relay unit 2 to flow to the suction side of the compressor 10 during a heating operation.
  • the refrigerant connection pipe 4a allows connection between a portion of the refrigerant pipe 4 between the first refrigerant flow switching device 11 and the check valve 13c and a portion of the refrigerant pipe 4 between the check valve 13a and the relay unit 2 in the outdoor unit 1.
  • the refrigerant connection pipe 4b allows connection between a portion of the refrigerant pipe 4 between the check valve 13c and the relay unit 2 and a portion of the refrigerant pipe 4 between heat-source-side heat exchanger 12 and the check valve 13a in the outdoor unit 1.
  • a use-side heat exchanger 35 is provided in each of the indoor units 3.
  • the use-side heat exchangers 35 are connected to heat medium flow control devices 34 and second heat medium flow switching devices 33 of the relay unit 2 by the pipes 5.
  • the use-side heat exchangers 35 exchange heat between air which is supplied from a blower device such as a fan, which is not illustrated in the drawing, and a heat medium, and generate heating air or cooling air to be supplied to the indoor space 7.
  • a duct 43 or the like is attached to the use-side heat exchangers 35.
  • the blower device which is not illustrated in the drawing, outdoor air is taken into the indoor space 7 via the duct 43, and ventilation may thus be attained.
  • Fig. 2 the case where the four indoor units 3 are connected to the relay unit 2 is illustrated as an example, and the indoor units 3 are illustrated as an indoor unit 3a, an indoor unit 3b, an indoor unit 3c, and an indoor unit 3d in this order from the top side of the drawing.
  • the use-side heat exchangers 35 are illustrated as a use-side heat exchanger 35a, a use-side heat exchanger 35b, a use-side heat exchanger 35c, and a use-side heat exchanger 35d in this order from the top side of the drawing.
  • the number of connected indoor units 3 is not necessarily four as illustrated in Fig. 2 .
  • the state in which the duct 43 is connected to the indoor unit 3a is illustrated as an example in Fig. 2
  • the number of indoor units 3 with which the duct 43 may be connected is not necessarily the indoor unit.
  • the duct 43 may be connected to any of the indoor units 3b to 3d.
  • the at least two or more intermediate heat exchangers 25, two expansion devices 26, two opening and closing devices (an opening and closing device 27 and an opening and closing device 29), two second refrigerant flow switching devices 28, two heat medium conveyance devices (hereinafter, referred to as the pumps 31), four first heat medium flow switching devices 32, the four second heat medium flow switching devices 33, and the four heat medium flow control devices 34 are provided.
  • the two intermediate heat exchangers 25 function as condensers (radiators) when supplying heating energy to an indoor unit 3 that is performing a heating operation and function as evaporators when supplying cooling energy to an indoor unit 3 that is performing a cooling operation, exchange heat between a heat-source-side refrigerant and a heat medium, and transmit cooling energy or heating energy generated at the outdoor unit 1 and stored in the heat-source-side refrigerant to the heat medium.
  • the intermediate heat exchanger 25a is provided between the expansion device 26a and the second refrigerant flow switching device 28a in the refrigerant circulation circuit A and is used for cooling a heat medium in a cooling and heating mixed operation mode.
  • the intermediate heat exchanger 25b is provided between the expansion device 26b and the second refrigerant flow switching device 28b in the refrigerant circulation circuit A and is used for heating a heat medium in a cooling and heating mixed operation mode.
  • the two expansion devices 26 (the expansion device 26a and the expansion device 26b) function as pressure reducing valves or expansion valves to decompress and expanse a heat-source-side refrigerant.
  • the expansion device 26a is provided on the upstream side of the intermediate heat exchanger 25a in the flow of a heat-source-side refrigerant for a cooling operation.
  • the expansion device 26b is provided on the upstream side of the intermediate heat exchanger 25b in the flow of a heat-source-side refrigerant for a cooling operation.
  • the two expansion devices 26 may be devices whose opening degree may be controlled in a variable manner, such as electronic expansion valves.
  • the two opening and closing devices are solenoid valves which may be opened and closed by electrical connection, and open and close the refrigerant pipes 4. That is, the two opening and closing devices are controlled to be opened and closed in accordance with an operation mode, and switch the flow passage of a heat-source-side refrigerant.
  • the opening and closing device 27 is provided at a portion of the refrigerant pipe 4 on a heat-source-side refrigerant inlet side (a portion of the refrigerant pipe 4 that connects the outdoor unit 1 with the relay unit 2 and that is located at the most bottom side in the drawing).
  • the opening and closing device 29 is provided at a pipe (bypass pipe 20) which connects the portion of the refrigerant pipe 4 on the heat-source-side refrigerant inlet side with a portion of the refrigerant pipe 4 on a heat-source-side refrigerant outlet side.
  • Devices whose opening degree may be controlled in a variable manner such as electrical expansion valves, may be used as the opening and closing device 27 and the opening and closing device 29, as long as the devices may switch a refrigerant flow passage.
  • the two second refrigerant flow switching devices 28 are, for example, four-way valves, and switch the flow of a heat-source-side refrigerant such that the intermediate heat exchangers 25 operate as condensers or evaporators in accordance with the operation mode.
  • the second refrigerant flow switching device 28a is provided on the downstream side of the intermediate heat exchanger 25a in the flow of a heat-source-side refrigerant for a cooling operation.
  • the second refrigerant flow switching device 28b is provided on the downstream side of the intermediate heat exchanger 25b in the flow of a heat-source-side refrigerant for a cooling only operation mode.
  • the two pumps 31 (the pump 31a and the pump 31b) cause a heat medium that flows through the pipes 5 to circulate to the heat medium circulation circuit B.
  • the pump 31a is provided at a portion of the pipe 5 between the intermediate heat exchanger 25a and the second heat medium flow switching devices 33.
  • the pump 31b is provided at a portion of the pipe 5 between the intermediate heat exchanger 25b and the second heat medium flow switching devices 33.
  • the two pumps 31 are, for example, pumps whose capacity can be controlled, and may be configured such that the flow rate of the pumps can be adjusted according to the size of the load in the indoor units 3.
  • the four first heat medium flow switching devices 32 are three-way valves or the like, and switch the flow passage of a heat medium between the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • the number of first heat medium flow switching devices 32 provided corresponds to the number of indoor units 3 installed (in this case, four).
  • the first heat medium flow switching devices 32 are provided on the outlet side of the heat medium flow passages for the use-side heat exchangers 35 in such a manner that one of the three ways is connected to the intermediate heat exchanger 25a, another one of the three ways is connected to the intermediate heat exchanger 25b, and the other one of the three ways is connected to the heat medium flow control devices 34.
  • first heat medium flow switching device 32a In association with the indoor units 3, they are illustrated as the first heat medium flow switching device 32a, the first heat medium flow switching device 32b, the first heat medium flow switching device 32c, and the first heat medium flow switching device 32d in this order from the top side of the drawing. Furthermore, switching of a heat medium flow passage includes partial switching from one side to the other side as well as full switching from one side to the other side.
  • the four second heat medium flow switching devices 33 are three-way valves or the like, and switch the flow passage of a heat medium between the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • the number of second heat medium flow switching devices 33 provided corresponds to the number of indoor units 3 installed (in this case, four).
  • the second heat medium flow switching devices 33 are provided on the inlet side of the heat medium flow passages for the use-side heat exchangers 35 in such a manner that one of the three ways is connected to the intermediate heat exchanger 25a, another one of the three ways is connected to the intermediate heat exchanger 25b, and the other one of the three ways is connected to the heat medium flow control devices 35.
  • switching of a heat medium flow passage includes partial switching from one side to the other side as well as full switching from one side to the other side.
  • the four heat medium flow control devices 34 are two-way valves or the like whose opening area can be controlled, and control the flow rate of a heat medium flowing in the pipes 5.
  • the number of heat medium flow control devices 34 provided corresponds to the number of indoor units 3 installed (in this case, four).
  • the heat medium flow control devices 34 are provided on the outlet side of the heat medium flow passages for the use-side heat exchangers 35 in such a manner that one of the two ways is connected to the use-side heat exchangers 35 and the other one of the two ways is connected to the first heat medium flow switching devices 32. That is, the heat medium flow control devices 34 adjust the amount of heat medium flowing into the indoor units 3 in accordance with the temperature of the heat medium flowing into and flowing out of the indoor units 3 and may thus supply to the indoor units 3 an optimal amount of heat medium for the indoor load.
  • the heat medium flow control devices 34 may be provided on the inlet side of the heat medium flow passages for the use-side heat exchangers 35. Furthermore, the heat medium flow control devices 34 may be provided at a portion that is on the inlet side of the heat medium flow passages for the use-side heat exchangers 35 and that is between the second heat medium flow switching devices 33 and the use-side heat exchangers 35. Moreover, when an indoor unit 3 requires no load, such as during stoppage or thermo-OFF, the supply of a heat medium to the indoor unit 3 may be stopped by fully closing the heat medium flow control devices 34.
  • the heat medium flow control devices 34 may be omitted.
  • temperature sensors 40 for detecting the temperature of a heat medium on the outlet side of the intermediate heat exchanger 25 are provided.
  • Information (temperature information) detected by the temperature sensors 40 is sent to a controller 50 that performs overall control of the operation of the air-conditioning apparatus 100, and is used for control of the driving frequency of the compressor 10, the rotation speed of a blower device, which is not illustrated in the drawing, switching of the first refrigerant flow switching device 11, the driving frequency of the pumps 31, switching of the second refrigerant flow switching devices 28, switching of the flow passage of a heat medium, adjustment of the flow rate of a heat medium in the indoor units 3, and the like.
  • controller 50 may be provided so as to be able to communicate with at least one of the outdoor unit 1, the indoor units 3, and the relay unit 2 or with the individual units.
  • the controller 50 is composed of a microcomputer or the like.
  • the controller 50 controls the individual actuators (driving parts including the pumps 31, the first heat medium flow switching devices 32, the second heat medium flow switching devices 33, the expansion devices 26, and the second refrigerant flow switching devices 28), such as the driving frequency of the compressor 10, the rotation speed of the blower device (including ON/OFF), switching of the first refrigerant flow switching device 11, driving of the pumps 31, the opening degree of the expansion devices 26, opening and closing of the opening and closing devices (the opening and closing device 27 and the opening and closing device 29), switching of the second refrigerant flow switching devices 28, switching of the first heat medium flow switching devices 32, switching of the second heat medium flow switching devices 33, and driving of the heat medium flow control devices 34, in accordance with detection information from the various detection units and instructions from a remote controller.
  • the individual actuators driving parts including the pumps 31, the first heat medium flow switching devices 32, the second heat medium flow switching devices 33, the expansion devices 26, and the second refrigerant flow switching devices 28
  • the individual actuators
  • the pipes 5 through which a heat medium flows include a pipe which is connected to the intermediate heat exchanger 25a and a pipe which is connected to the intermediate heat exchanger 25b.
  • Each of the pipes 5 branches out into branch pipes (in this example, four branches) in accordance with the number of indoor units 3 connected to the relay unit 2.
  • the pipes 5 are connected to the first heat medium flow switching devices 32 and the second heat medium flow switching devices 33.
  • the first heat medium flow switching devices 32 and the second heat medium flow switching devices 33 are controlled to determine whether a heat medium from the intermediate heat exchanger 25a or a heat medium from the intermediate heat exchanger 25b is to be caused to flow into the use-side heat exchangers 35.
  • the refrigerant circulation circuit A is formed by connecting the compressor 10, the first refrigerant flow switching device 11, the heat-source-side heat exchanger 12, the opening and closing device 27, the opening and closing device 29, the second refrigerant flow switching devices 28, the refrigerant flow passages for the intermediate heat exchangers 25, the expansion devices 26, and the accumulator 19 by the refrigerant pipes 4.
  • the heat medium circulation circuit B is formed by connecting the heat medium flow passages for the intermediate heat exchangers 25, the pumps 31, the first heat medium flow switching devices 32, the heat medium flow control devices 34, the use-side heat exchangers 35, and the second heat medium flow switching devices 33 by the pipes 5. That is, the plurality of use-side heat exchangers 35 are connected in parallel to each of the intermediate heat exchangers 25 to form the heat medium circulation circuit B as multiple systems.
  • the outdoor unit 1 and the relay unit 2 are connected via the intermediate heat exchanger 25a and the intermediate heat exchanger 25b which are provided in the relay unit 2, and the relay unit 2 and the indoor units 3 are connected via the intermediate heat exchanger 25a and the intermediate heat exchanger 25b. That is, in the air-conditioning apparatus 100, heat is exchanged at the intermediate heat exchanger 25a and the intermediate heat exchanger 25b between a heat-source-side refrigerant which circulates through the refrigerant circulation circuit A and a heat medium which circulates through the heat medium circulation circuit B. With the use of the above configuration, the air-conditioning apparatus 100 achieves an optimal cooling operation or an optimal heating operation for the indoor load.
  • the air-conditioning apparatus 100 is able to cause the indoor unit 3 to perform a cooling operation or a heating operation. That is, the air-conditioning apparatus 100 is configured such that not only may all of the indoor units 3 perform the same operation but also the indoor units 3 may perform different operations.
  • Operation modes executed by the air-conditioning apparatus 100 include a heating only operation mode in which all of the driving indoor units 3 perform a heating operation, a cooling only operation mode in which all of the driving indoor units 3 perform a cooling operation, a heating main operation mode, which is a cooling and heating mixed operation mode in which the heating load is larger than the cooling load, and a cooling main operation mode, which is a cooling and heating mixed operation mode in which the cooling load is larger than heating load. Furthermore, in the heating only operation mode and the heating main operation mode, a defrosting operation mode is available for removing frost attached at the heat-source-side heat exchanger 12 as a result of heat exchange with the outdoor air at the heat-source-side heat exchanger 12. The individual operation modes will be described below in accordance with the flow of a heat-source-side refrigerant and a heat medium.
  • Fig. 3 is a refrigerant circuit diagram illustrating the flow of refrigerant in the cooling only operation mode of the air-conditioning apparatus 100.
  • the cooling only operation mode will be explained in accordance with an example of the case where a cooling load is generated at all of the use-side heat exchangers 35a to 35d.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant flows.
  • solid arrows represent the flow direction of a heat-source-side refrigerant, and broken arrows represent the flow direction of a heat medium.
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven and the heat medium flow control devices 34a to 34d are opened, so that a heat medium may circulate between each of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b and the use-side heat exchangers 35a to 35d.
  • the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b are switched to the side of cooling operation, the opening and closing device 27 is opened, and the opening and closing device 29 is closed.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11 through the heat-source-side heat exchanger 12, is subjected to heat exchange with air in the outdoor space 6 (hereinafter, referred to as outdoor air), turns into a high-temperature and high-pressure liquid or two-phase refrigerant, passes through the check valve 13a, flows through the refrigerant connection pipe 4a, and flows out of the outdoor unit 1.
  • the high-temperature and high-pressure liquid or two-phase refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the high-temperature and high-pressure liquid or two-phase refrigerant which has flowed into the relay unit 2 passes through the opening and closing device 27, is split, and is expanded at the expansion device 26a and the expansion device 26b into low-temperature and low-pressure two-phase refrigerant flows.
  • the two-phase refrigerant flows flow into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b, evaporate and liquefy while receiving heat from a heat medium circulating in the heat medium circulation circuit B, and turn into low-temperature gas refrigerant.
  • the opening degree of the expansion devices 26 is controlled such that the superheat (degree of superheat) obtained as a difference between the value obtained by converting the pressure of a heat-source-side refrigerant flowing between the intermediate heat exchangers 25 and the expansion devices 26 into saturation temperature and the temperature on the outlet side of the intermediate heat exchangers 25 is constant. If the temperature at the intermediate position of the intermediate heat exchangers 25 can be measured, the saturation temperature obtained by conversion of the temperature at the intermediate position may be used instead. In this case, there is no need to install a pressure sensor, and the system can be configured at low cost.
  • the cooling energy of a heat-source-side refrigerant is transferred to a heat medium at both of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b, the cooled heat medium is pressurized at and flows out of the pump 31a and the pump 31b, and flows into the use-side heat exchangers 35a to 35d via the second heat medium flow switching devices 33a to 33d. Then, the heat medium receives heat from the indoor air at the use-side heat exchangers 35a to 35d, and cooling of the indoor space 7 is thus performed.
  • the heat medium flows out of the use-side heat exchangers 35a to 35d, and flows into the heat medium flow control devices 34a to 34d.
  • the flow rate of a heat medium is controlled to a flow rate necessary for an air-conditioning load required for the indoor space, and the heat medium is thus caused to flow into the use-side heat exchangers 35a to 35d.
  • the heat medium which has flowed out of the heat medium flow control devices 34a to 34d passes through the first heat medium flow switching devices 32a to 32d, flows into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b, delivers to a refrigerant side the amount of heat received from the indoor space 7 through the indoor units 3, and is sucked again into the pump 31a and the pump 31b.
  • a heat medium flows in the direction from the second heat medium flow switching devices 33 via the heat medium flow control devices 34 to the first heat medium flow switching devices 32.
  • the air-conditioning load required for the indoor space 7 may be carried by controlling the temperature detected by the temperature sensors 40 or the difference between the temperature detected by the temperature sensors 40 and the temperature of a heat medium flowing out of the use-side heat exchangers 35 to be maintained at a target value.
  • the outlet temperature of the intermediate heat exchangers 25 any one of the temperature of the temperature sensor 40a and the temperature of the temperature sensor 40b or the average of these temperatures may be used.
  • the first heat medium flow switching devices 32 and the second heat medium flow switching devices 33 may be controlled to intermediate opening degrees or opening degrees corresponding to the heat medium temperature at the outlet of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b so that the flow passages for the flow to both of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b are secured.
  • the use-side heat exchangers 35 should be controlled based on the temperature difference between the inlet and outlet thereof. However, since the heat medium temperature on the inlet side of the use-side heat exchangers 35 is substantially the same as the temperature detected by the temperature sensors 40. Therefore, with the use of the temperature sensors 40, the number of temperature sensors may be reduced, and the system may thus be configured at low cost.
  • Fig. 4 is a refrigerant circuit diagram illustrating the flow of refrigerant in the heating only operation mode of the air-conditioning apparatus 100.
  • the heating only operation mode will be explained in accordance with an example of the case where a heating load is generated at all of the use-side heat exchangers 35a to 35d.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant flows.
  • solid arrows represent the flow direction of a heat-source-side refrigerant, and broken arrows represent the flow direction of a heat medium.
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the relay unit 2 without passing through the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven and the heat medium flow control devices 34a to 34d are opened, so that a heat medium may circulate between each of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b and the use-side heat exchangers 35a to 35d.
  • the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b are switched to the side of heating operation, the opening and closing device 27 is closed, and the opening and closing device 29 is opened.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11, flows through the refrigerant connection pipe 4a, passes through the check valve 13d, and flows out of the outdoor unit 1.
  • the high-temperature and high-pressure gas refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the high-temperature and high-pressure gas refrigerant which has flowed into the relay unit 2 is split.
  • the split gas refrigerant flows pass through the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b, and flow into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • the high-temperature and high pressure gas refrigerant flows which have flowed into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b condense and liquefy while transferring heat to a heat medium circulating in the heat medium circulation circuit B, and turn into high-pressure liquid refrigerant flows.
  • the liquid refrigerant flows that have flowed out of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b are expanded at the expansion device 26a and the expansion device 26b into low-temperature and low-pressure, two-phase refrigerant flows. These two-phase refrigerant flows are merged together.
  • the merged two-phase refrigerant passes through the opening and closing device 29, flows out of the relay unit 2, passes through the refrigerant pipe 4, and flows into the outdoor unit 1 again.
  • the refrigerant which has flowed into the outdoor unit 1 flows through the refrigerant connection pipe 4b, passes through the check valve 13b, and flows into the heat-source-side heat exchanger 12 operating as an evaporator.
  • the heat-source-side refrigerant which has flowed into the heat-source-side heat exchanger 12 receives heat from the outdoor air at the heat-source-side heat exchanger 12, and turns into a low-temperature and low-pressure gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant which has flowed out of the heat-source-side heat exchanger 12 is sucked into the compressor 10 again via the first refrigerant flow switching device 11 and the accumulator 19.
  • the opening degree of the expansion devices 26 is controlled such that the subcooling (degree of subcooling) obtained as a difference between the value obtained by converting the pressure of a heat-source-side refrigerant flowing between the intermediate heat exchangers 25 and the expansion devices 26 into saturation temperature and the temperature on the outlet side of the intermediate heat exchangers 25 is constant. If the temperature at the intermediate position of the intermediate heat exchangers 25 can be measured, the temperature at the intermediate position may be used instead of the converted saturation temperature. In this case, there is no need to install a pressure sensor, and the system can be configured at low cost.
  • the heating energy of a heat-source-side refrigerant is transferred to a heat medium at both of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b, and the heated heat medium is caused by the pump 31a and the pump 31b to flow in the pipes 5.
  • the heat medium which has been pressurized at and flowed out of the pump 31a and the pump 31b flows into the use-side heat exchangers 35a to 35d via the second heat medium flow switching devices 33a to 33d. Then, the heat medium transfers heat to the indoor air at the use-side heat exchangers 35a to 35d, and heating of the indoor space 7 is thus performed.
  • the heat medium flows out of the use-side heat exchangers 35a to 35d, and flows into the heat medium flow control devices 34a to 34d.
  • the flow rate of a heat medium is controlled to a flow rate necessary for an air-conditioning load required for an indoor space, and the heat medium is thus caused to flow into the use-side heat exchangers 35a to 35d.
  • the heat medium which has flowed out of the heat medium flow control devices 34a to 34d passes through the first heat medium flow switching devices 32a to 32d, flows into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b, receives the amount of heat supplied to the indoor space 7 through the indoor units 3, and is sucked again into the pump 31a and the pump 31b.
  • a heat medium flows in the direction from the second heat medium flow switching devices 33 via the heat medium flow control devices 34 to the first heat medium flow switching devices 32.
  • the air-conditioning load required for the indoor space 7 may be carried by performing control so that the temperatures detected by the temperature sensors 40 or the difference between the temperatures detected by the temperature sensors 40 and the temperature of a heat medium flowing out of the use-side heat exchangers 35 to be maintained at a target value.
  • the outlet temperature of the intermediate heat exchangers 25 any one of the temperature of the temperature sensor 40a and the temperature of the temperature sensor 40b or the average of these temperatures may be used.
  • the first heat medium flow switching devices 32 and the second heat medium flow switching devices 33 may be controlled to intermediate opening degrees or opening degrees corresponding to the heat medium temperature at the outlet of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b so that the flow passages for the flow to both of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b are secured.
  • the use-side heat exchangers 35 should be controlled based on the temperature difference between the inlet and outlet thereof. However, since the heat medium temperature on the inlet side of the use-side heat exchangers 35 is substantially the same as the temperature detected by the temperature sensors 40. Therefore, with the use of the temperature sensors 40, the number of temperature sensors may be reduced, and the system may thus be configured at low cost.
  • Fig. 5 is a refrigerant circuit diagram illustrating the flow of refrigerant in the cooling and heating mixed operation mode of the air-conditioning apparatus 100.
  • the heating main operation mode of a cooling and heating mixed operation in which a heating load is generated in some of the use-side heat exchangers 35 and a cooling load is generated in the rest of use-side heat exchangers 35 will be explained.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant circulates.
  • solid arrows represent the flow direction of a heat-source-side refrigerant
  • broken arrows represent the flow direction of a heat medium.
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the relay unit 2 without passing through the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven and the heat medium flow control devices 34a to 34d are opened, so that a heat medium may circulate between the intermediate heat exchanger 25a and the use-side heat exchanger 35 at which the cooling load is generated and between the intermediate heat exchanger 25b and the use-side heat exchanger 35 at which the heating load is generated.
  • the second refrigerant flow switching device 28a is switched to the side of cooling operation, the second refrigerant flow switching device 28b is switched to the side of heating operation, the expansion device 26a is fully opened, the opening and closing device 27 is closed, and the opening and closing device 29 is closed.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11, flows through the refrigerant connection pipe 4a, passes through the check valve 13d, and flows out of the outdoor unit 1.
  • the high-temperature and high-pressure gas refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the high-temperature and high-pressure gas refrigerant which has flowed into the relay unit 2 passes through the second refrigerant flow switching device 28b, and flows into the intermediate heat exchanger 25b that operates as a condenser.
  • the gas refrigerant which has flowed into the intermediate heat exchanger 25b condenses and liquefies while transferring heat to a heat medium circulating in the heat medium circulation circuit B, and turns into a liquid refrigerant.
  • the liquid refrigerant that has flowed out of the intermediate heat exchanger 25b is expanded at the expansion device 26b into a low-pressure, two-phase refrigerant.
  • the low-pressure, two-phase refrigerant passes through the expansion device 26a and flows into the intermediate heat exchanger 25a that operates as an evaporator.
  • the low-pressure, two-phase refrigerant that has flowed into the intermediate heat exchanger 25a evaporates by receiving heat from a heat medium circulating in the heat medium circulation circuit B, and thus cools the heat medium.
  • the low-pressure, two-phase refrigerant flows out of the intermediate heat exchanger 25a passes through the second refrigerant flow switching device 28a, flows out of the relay unit 2, passes through the refrigerant pipe 4, and flows into
  • the low-temperature and low-pressure, two-phase refrigerant which has flowed into the outdoor unit 1 passes through the check valve 13b, and flows into the heat-source-side heat exchanger 12 that operates as an evaporator. Then, the refrigerant which has flowed into the heat-source-side heat exchanger 12 receives heat from the outdoor air at the heat-source-side heat exchanger 12, and turns into a low-temperature and low-pressure gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant which has flowed out of the heat-source-side heat exchanger 12 is sucked into the compressor 10 again via the first refrigerant flow switching device 11 and the accumulator 19.
  • the opening degree of the expansion device 26b is controlled such that the subcooling (the degree of subcooling) of the refrigerant at the outlet of the intermediate heat exchanger 25b is a target value.
  • subcooling may be controlled using the expansion device 26a.
  • the heating energy of a heat-source-side refrigerant is transferred to a heat medium at the intermediate heat exchanger 25b, and the heated heat medium is caused by the pump 31b to flow in the pipe 5. Furthermore, in the heating main operation mode, the cooling energy of a heat-source-side refrigerant is transferred to a heat medium at the intermediate heat exchanger 25a, and the cooled heat medium is caused by the pump 31 a to flow in the pipe 5.
  • the cooled heat medium which has been pressurized by and flowed out of the pump 31a flows via the second heat medium flow switching device 33 into the use-side heat exchanger 35 at which the cooling load is generated, and the heat medium which has been pressurized by and flowed out of the pump 31b flows via the second heat medium flow switching device 33 into the use-side heat exchanger 35 at which the heating load is generated.
  • the second heat medium flow switching device 33 is switched to a direction in which the intermediate heat exchanger 25b and the pump 31b are connected when the connected indoor unit 3 is in the heating operation mode, and is switched to a direction in which the intermediate heat exchanger 25a and the pump 31a are connected when the connected indoor unit 3 is in the cooling operation mode. That is, the second heat medium flow switching devices 33 allow a heat medium to be supplied to the indoor units 3 to be used for heating or cooling.
  • the use-side heat exchangers 35 perform a cooling operation for the indoor space 7 by causing a heat medium to receive heat from the indoor air or a heating operation for the indoor space 7 by causing a heat medium to transfer heat to the indoor space.
  • the flow rate of a heat medium is controlled to a flow rate necessary for an air-conditioning load required for an indoor space, and the heat medium is thus caused to flow into the use-side heat exchangers 35.
  • the heat medium whose temperature is slightly increased by being used for a cooling operation and passing through the use-side heat exchanger 35 passes through the heat medium flow control device 34 and the first heat medium flow switching device 32, flows into the intermediate heat exchanger 25a, and is sucked into the pump 31a again.
  • the heat medium whose temperature is slightly decreased by being used for a heating operation and passing through the use-side heat exchanger 35 passes through the heat medium flow control device 34 and the first heat medium flow switching device 32, flows into the intermediate heat exchanger 25b, and is sucked into the pump 31a again.
  • the first heat medium flow switching device 32 is switched to a direction in which the intermediate heat exchanger 25b and the pump 31b are connected when the connected indoor unit 3 is in the heating operation mode, and is switched to a direction in which the intermediate heat exchanger 25a and the pump 31a are connected when the connected indoor unit 3 is in the cooling operation mode.
  • the hot heat medium and the cold heat medium are not mixed together by the operation of the first heat medium flow switching devices 32 and the second heat medium flow switching devices 33, and are introduced to the use-side heat exchangers 35 at which the heating load and the cooling load exist. Accordingly, the heat medium that has been used for the heating operation mode is caused to flow into the intermediate heat exchanger 25b at which a refrigerant transfers heat for heating, and the heat medium that has been used for the cooling operation mode is caused to flow into the intermediate heat exchanger 25a at which a refrigerant receives heat for cooling. Then, each of the heat media is subjected to heat exchange with a refrigerant, and is transferred to the pump 31a and the pump 31b.
  • a heat medium flows in the direction from the second heat medium flow switching devices 33 via the heat medium flow control devices 34 to the first heat medium flow switching devices 32.
  • the air-conditioning load required for the indoor space 7 may be carried by controlling, for the side of heating operation, the difference between the temperature detected by the temperature sensor 40b and the temperature of a heat medium which has flowed out of the use-side heat exchanger 35, and for the side of cooling operation, the difference between the temperature of a heat medium which has flowed out of the use-side heat exchanger 35 and the temperature detected by the temperature sensor 40a to be maintained at a target value.
  • the flow of a heat-source-side refrigerant in the refrigerant circulation circuit A and the flow of a heat medium in the heat medium circulation circuit B are similar to those in the heating main operation mode.
  • the heat-source-side heat exchanger 12 in the outdoor unit 1 operates as an evaporator to exchange heat with the outdoor air. Therefore, if the outdoor air temperature is low, the evaporating temperature of the heat-source-side heat exchanger 12 decreases, and frosting occurs to the surface of the heat-source-side heat exchanger 12 due to the moisture of the outdoor air. Consequently, the performance of heat exchange may be degraded. In the air-conditioning apparatus 100, for example, the outdoor unit 1 detects evaporating temperature.
  • the defrosting operation mode for removing frost on the surface of the heat-source-side heat exchanger 12 is executed.
  • the heating only operation mode and the heating main operation mode correspond to the "heating operation mode" in the present invention.
  • the air-conditioning apparatus 100 in execution of the defrosting operation mode, the heat capacity that has been held by a heat medium in the heating operation may be used. That is, during the heating operation mode, the air-conditioning apparatus 100 can melt frost formed around the heat-source-side heat exchanger 12 by switching the first refrigerant flow switching device 11 to the side of cooling operation, causing at least one of the pumps 31 to operate, and causing a refrigerant to receive heat held by a heat medium in at least one of the intermediate heat exchangers 25 (heat recovery defrosting operation mode). With the above operation, the air-conditioning apparatus 100 is able to remove frost on the surface of the heat-source-side heat exchanger 12 more quickly than conventional techniques. Meanwhile, the air-conditioning apparatus 100 is able to continue execution of the heating operation mode in the use-side heat exchangers 35.
  • the air-conditioning apparatus 100 has a bypass defrosting operation mode for melting frost formed around the heat-source-side heat exchanger 12 by switching the first refrigerant flow switching device 11 to the side of cooling operation to cause part or whole of the refrigerant to flow to the bypass pipe 20 during the heating operation mode.
  • the air-conditioning apparatus 100 increases the temperature of a heat medium through the intermediate heat exchangers 25 during the heating operation mode immediately before execution of the defrosting operation mode. Then, after detecting that the temperature of the heat medium whose temperature has been increased and which is detected by the temperature sensors 40 is higher than a setting temperature (for example, 43 degrees Centigrade), the air-conditioning apparatus 100 executes the defrosting operation mode. With the above operation, the air-conditioning apparatus 100 may ensure the heat capacity to be used for the defrosting operation mode and the amount of heat for continuing the heating operation mode.
  • the air-conditioning apparatus 100 executes the "heat recovery defrosting operation mode" which utilizes the heat capacity held by the heat medium.
  • the air-conditioning apparatus 100 executes the "bypass defrosting operation mode" which does not utilize the heat capacity held by the heat medium.
  • the setting temperature may be changed to any temperature.
  • a use-side air temperature sensor for detecting the temperature of air blown to the use-side heat exchangers 35 and set the setting temperature to a value equal to or higher than the temperature detected by the use-side air temperature sensor.
  • the defrosting operation mode executed by the air-conditioning apparatus 100 includes two types of defrosting operation modes (the "heat recovery defrosting operation mode” and the “bypass defrosting operation mode”) according to the flow of a heat-source-side refrigerant.
  • the "heat recovery defrosting operation mode" that is executed during the heating only operation mode will be referred to as a "first heat recovery defrosting operation mode”.
  • the "heat recovery defrosting operation mode" that is executed during the heating main operation mode will be referred to as a "second heat recovery defrosting operation mode”.
  • bypass defrosting operation mode that is executed during the heating only operation mode will be referred to as a "first bypass defrosting operation mode".
  • bypass defrosting operation mode that is executed during the heating main operation mode will be referred to as a "second bypass defrosting operation mode".
  • the "first heat recovery defrosting operation mode" executed during the heating only operation mode of the air-conditioning apparatus 100 further includes two types of defrosting operation modes (a “first heat recovery defrosting operation mode (1)” and a “first heat recovery defrosting operation mode (2)”) according to the flow of a heat-source-side refrigerant.
  • Fig. 6 is a refrigerant circuit diagram illustrating the flow of refrigerant and the flow of a heat medium in the "first heat recovery defrosting operation mode (1)" of the air-conditioning apparatus 100.
  • the "first heat recovery defrosting operation mode (1)" will be explained.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant circulates.
  • solid arrows represent the flow direction of a heat-source-side refrigerant
  • broken arrows represent the flow direction of a heat medium.
  • the "first heat recovery defrosting operation mode (1)" is a defrosting operation mode to be executed during the heating only operation mode of the air-conditioning apparatus 100 when frosting occurs to the heat-source-side heat exchanger 12 in the outdoor unit 1 due to moisture of the outdoor air and the evaporating temperature decreases.
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven and the heat medium flow control devices 34a to 34d are opened, so that a heat medium may circulate between each of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b and the use-side heat exchangers 35a to 35d.
  • the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b are switched to the side of cooling operation, the opening and closing device 27 is opened, and the opening and closing device 29 is closed.
  • the expansion device 26a and the expansion device 26b are fully opened. However, the expansion device 26a and the expansion device 26b are not necessarily strictly fully opened.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11, and flows into the heat-source-side heat exchanger 12.
  • the refrigerant that has flowed into the heat-source-side heat exchanger 12 exchanges heat with a frosting part on the heat-source-side heat exchanger 12.
  • the frosting part on the heat-source-side heat exchanger 12 is melted by the high-temperature, high-pressure refrigerant.
  • the low-temperature and high-pressure refrigerant that has exchanged heat with the frosting part on the heat-source-side heat exchanger 12 passes through the check valve 13a, and then flows out of the outdoor unit 1.
  • the low-temperature and high-pressure refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the refrigerant which has flowed into the relay unit 2 passes through the opening and closing device 27, and is split.
  • the split refrigerant flows pass through the expansion device 26a and the expansion device 26b and flow into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • the low-temperature and high-pressure refrigerant flows which have flowed into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b are subjected to heat exchange with a heat medium which has been used for heating and turn into high-temperature, high-pressure refrigerant flows.
  • Fig. 7 is a refrigerant circuit diagram illustrating the flow of refrigerant and the flow of a heat medium in the "first heat recovery defrosting operation mode (2)" of the air-conditioning apparatus 100.
  • the "first heat recovery defrosting operation mode (2)" will be explained.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant circulates.
  • solid arrows represent the flow direction of a heat-source-side refrigerant
  • broken arrows represent the flow direction of a heat medium.
  • the "first heat recovery defrosting operation mode (2)” is a defrosting operation mode to be executed during the heating only operation mode of the air-conditioning apparatus 100 when frosting occurs to the heat-source-side heat exchanger 12 in the outdoor unit 1 due to moisture of the outdoor air and the evaporating temperature decreases.
  • the flow of a heat-source-side refrigerant in the "first heat recovery defrosting operation mode (2)” differs from that in the "first heat recovery defrosting operation mode (1)”.
  • the air-conditioning apparatus 100 may select any one of the "first heat recovery defrosting operation mode (1)” and the "first heat recovery defrosting operation mode (2)".
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven and the heat medium flow control devices 34a to 34d are opened, so that a heat medium may circulate between each of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b and the use-side heat exchangers 35a to 35d.
  • both of the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b maintain the opening direction on the side of heating operation, the opening and closing device 27 is closed, and the opening and closing device 29 is opened.
  • the expansion device 26a and the expansion device 26b are fully opened. However, the expansion device 26a and the expansion device 26b are not necessarily strictly fully opened.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11, and flows into the heat-source-side heat exchanger 12.
  • the refrigerant that has flowed into the heat-source-side heat exchanger 12 exchanges heat with a frosting part on the heat-source-side heat exchanger 12.
  • the frosting part on the heat-source-side heat exchanger 12 is melted by the high-temperature, high-pressure refrigerant.
  • the low-temperature and high-pressure refrigerant that has exchanged heat with the frosting part on the heat-source-side heat exchanger 12 passes through the check valve 13a, and then flows out of the outdoor unit 1.
  • the low-temperature and high-pressure gas refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the low-temperature and high-pressure gas refrigerant which has flowed into the relay unit 2 is split.
  • the split gas refrigerant flows pass through the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b, and flow into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • the low-temperature and high-pressure refrigerant flows which have flowed into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b are subjected to heat exchange with a heat medium which has been used for heating and turn into high-temperature, high-pressure refrigerant flows.
  • a heat medium is subjected to heat exchange with a low-temperature and high-pressure gas refrigerant at both of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b and turns into a low-temperature heat medium.
  • the heat medium whose temperature has been decreased at the intermediate heat exchanger 25a and the intermediate heat exchanger 25b is pressurized by the pump 31a and the pump 31b, and flows into the use-side heat exchangers 35a to 35d via the second heat medium flow switching devices 33a to 33d.
  • the opening degree of the second heat medium flow switching devices 33 is controlled to an intermediate opening degree or an opening degree corresponding to the heat medium temperature at the outlet of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b so that the heat medium conveyed from both of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b may be supplied to the indoor units 3.
  • the heat medium flows out of the use-side heat exchangers 35a to 35d, and flows into the heat medium flow control devices 34a to 34d.
  • the heat medium which has flowed out of the heat medium flow control devices 34a to 34d passes through the first heat medium flow switching devices 32a to 32d.
  • the same opening degree adjustment as the second heat medium flow switching devices 33 is performed on the first heat medium flow switching devices 32, and the heat medium flow control devices 34 are fully opened.
  • the heat medium which has passed through the first heat medium flow switching devices 32a to 32d flows into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b, and is subjected to heat exchange again with flows of refrigerant flowing in the intermediate heat exchanger 25a and the intermediate heat exchanger 25b. After the amount of heat of the heat medium is supplied to the refrigerant side, the heat medium is sucked into the pump 31a and the pump 31b again.
  • the indoor unit 3 that has been performing a heating operation in the "first heat recovery defrosting operation mode" receives information indicating that the outdoor unit 1 is in the defrosting operation mode, and stops a blower device (hereinafter, simply referred to as a fan") for blowing air to the use-side heat exchanger 35.
  • a blower device hereinafter, simply referred to as a fan
  • the indoor air temperature and the indoor-unit blown-out air temperature may be detected, no problem occurs if the fan continues operating as far as the indoor unit blown-out air temperature is not lower than the indoor air temperature.
  • the fan may continue to operate as long as the heat medium temperature at the outlet of the intermediate heat exchanger 25 detected by the temperature sensor 40 is not lower than the indoor air temperature.
  • the amount of heat supplied from the heat medium to the refrigerant side may be supplied to the heat-source-side heat exchanger 12 of the outdoor unit 1. Therefore, the time for melting frost may be shortened.
  • Fig. 8 is a refrigerant circuit diagram illustrating the flow of refrigerant and the flow of a heat medium in the "second heat recovery defrosting operation mode" of the air-conditioning apparatus 100.
  • the "second heat recovery defrosting operation mode" will be explained.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant circulates.
  • solid arrows represent the flow direction of a heat-source-side refrigerant
  • broken arrows represent the flow direction of a heat medium.
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven, the heat medium flow control device 34 for the indoor unit 3 that is performing a cooling operation is opened so that a heat medium may circulate between the intermediate heat exchanger 25a and the use-side heat exchanger 35 of the indoor unit 3 that is performing the cooling operation, and the heat medium flow control device 34 for the indoor unit 3 that is performing a heating operation so that a heat medium may circulate between the intermediate heat exchanger 25b and the use-side heat exchanger 35 of the indoor unit 3 that is performing the heating operation.
  • both of the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b maintain the opening direction on the side of cooling operation, the opening and closing device 27 is opened, and the opening and closing device 29 is closed.
  • the expansion device 26a is controlled such that the refrigerant at the outlet of the intermediate heat exchanger 25a becomes a gas state, and the expansion device 26b is fully opened.
  • the expansion device 26b is not necessarily strictly fully opened.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11, and flows into the heat-source-side heat exchanger 12.
  • the refrigerant that has flowed into the heat-source-side heat exchanger 12 exchanges heat with a frosting part on the heat-source-side heat exchanger 12.
  • the frosting part on the heat-source-side heat exchanger 12 is melted by the high-temperature, high-pressure refrigerant.
  • the low-temperature and high-pressure refrigerant that has exchanged heat with the frosting part on the heat-source-side heat exchanger 12 passes through the check valve 13a, and then flows out of the outdoor unit 1.
  • the low-temperature and high-pressure refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the refrigerant which has flowed into the relay unit 2 passes through the opening and closing device 27, and is split.
  • the split refrigerant flows pass through the expansion device 26a and the expansion device 26b and flow into the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • the intermediate heat exchanger 25a due to the operation of the expansion device 26a, heat exchange with a heat medium continues to be performed to generate a low-temperature heat medium for cooling, and the generated low-temperature heat medium for cooling is supplied to the indoor unit 3. Meanwhile, a heat-source-side refrigerant whose heat capacity has been lost by defrosting of the heat-source-side heat exchanger 12 is conveyed to the intermediate heat exchanger 25b.
  • the heat medium whose temperature has been decreased at the intermediate heat exchanger 25a and the heat medium whose temperature has been decreased at the intermediate heat exchanger 25b are pressurized by the pump 31a and the pump 31b, and flow into the use-side heat exchangers 35a to 35d via the second heat medium flow switching devices 33a to 33d.
  • the second heat medium flow switching device 33 is switched to a direction in which the intermediate heat exchanger 25b and the pump 31b are connected when the connected indoor unit 3 is in the heating operation mode, and is switched to a direction in which the intermediate heat exchanger 25a and the pump 31a are connected when the connected indoor unit 3 is in the cooling operation mode.
  • the cooling operation continues to be performed by causing the heat medium which has been caused by the pump 31a to flow into the indoor unit 3 to be subjected to heat exchange with the indoor air of the indoor space 7 at the use-side heat exchanger 35. Then, the heat medium which has been subjected to heat exchange at the use-side heat exchanger 35 is conveyed into the relay unit 2 via the heat medium pipe 5 and the heat medium flow control device 34. The flow rate of the heat medium which has been conveyed to each of the indoor units 3 is adjusted by the corresponding heat medium flow control device 34. The heat medium which has flowed out of the heat medium flow control device 34 passes through the first heat medium flow switching devices 32.
  • the flow rate is adjusted at the heat medium flow control device 34 based on a detected difference between the temperature immediately before the pump 31a and the outlet temperature of the connected indoor unit 3. Furthermore, the first heat medium flow switching device 32 is switched to the direction in which the intermediate heat exchanger 25a and the pump 31a are connected.
  • the pump 31b is driven, the fan of the indoor unit 3 that has been executing the heating operation mode is stopped, and the heating operation mode is thus stopped. Furthermore, the second heat medium flow switching device 33 that is connected to the indoor unit 3 that has been executing the heating operation mode is directed toward the opening direction in which the connected pump 31b is connected. Moreover, the heat medium flow control device 34 after passing through the use-side heat exchanger 35 is fully opened, and the opening degree of the first heat medium flow switching device 32 is set to the same opening degree of the second heat medium flow switching device 33.
  • the heat medium that has been conveyed to the indoor unit 3 that has been executing the heating operation mode is conveyed to the intermediate heat exchanger 25b via the first heat medium flow switching device 32, without being subjected to heat exchange at the use-side heat exchanger 35.
  • the heat medium that has flowed into the intermediate heat exchanger 25b is subjected to heat exchange again with a heat-source-side refrigerant that has flowed into the intermediate heat exchanger 25b, and supplies the heat to the refrigerant side. After that, the heat medium is sucked again into the pump 31b.
  • the indoor unit 3 that has been performing a heating operation in the "second heat recovery defrosting operation mode" receives information indicating that the outdoor unit 1 is in the defrosting operation mode, and stops the fan. However, if the indoor air temperature and the indoor unit blown-out air temperature may be detected, no problem occurs if the fan continues operating as far as the indoor unit blown-out air temperature is not lower than the indoor air temperature. Furthermore, the fan may continue operating as long as the heat medium temperature at the outlet of the intermediate heat exchanger 25 detected by the temperature sensor 40 is not lower than the indoor air temperature.
  • Fig. 9 is a refrigerant circuit diagram illustrating the flow of refrigerant and the flow of a heat medium in the "first bypass defrosting operation mode" of the air-conditioning apparatus 100.
  • the "first bypass defrosting operation mode" will be explained.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant circulates.
  • solid arrows represent the flow direction of a heat-source-side refrigerant
  • broken arrows represent the flow direction of a heat medium.
  • the "first bypass defrosting operation mode” is a defrosting operation mode to be executed during the heating only operation mode of the air-conditioning apparatus 100 when frosting occurs to the heat-source-side heat exchanger 12 in the outdoor unit 1 due to moisture of the outdoor air and the evaporating temperature decreases.
  • the refrigerant does not receive the heat capacity from the heat medium.
  • the “first bypass defrosting operation mode” is executed during the execution of the "first heat recovery defrosting operation mode” by being switched according to a change in the setting temperature.
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven and the heat medium flow control devices 34a to 34d are opened, so that a heat medium may circulate between each of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b and the use-side heat exchangers 35a to 35d.
  • the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b maintain a state being switched to the side of cooling operation, the opening and closing device 27 is opened, and the opening and closing device 29 is closed.
  • the expansion device 26a and the expansion device 26b are fully closed.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11, and flows into the heat-source-side heat exchanger 12.
  • the refrigerant that has flowed into the heat-source-side heat exchanger 12 exchanges heat with a frosting part on the heat-source-side heat exchanger 12.
  • the frosting part on the heat-source-side heat exchanger 12 is melted by the high-temperature, high-pressure refrigerant.
  • the low-temperature and high-pressure refrigerant that has exchanged heat with the frosting part on the heat-source-side heat exchanger 12 passes through the check valve 13a, and then flows out of the outdoor unit 1.
  • the low-temperature and high-pressure refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the refrigerant which has flowed into the relay unit 2 passes through the opening and closing device 27, and then passes through the opening and closing device 29.
  • the expansion device 26a and the expansion device 26b are fully closed. Therefore, no refrigerant is conveyed to the intermediate heat exchanger 25a and the intermediate heat exchanger 25b.
  • the refrigerant which has passed through the opening and closing device 29 directly flows out of the relay unit 2, passes through the refrigerant pipe 4, and flows into the outdoor unit 1.
  • the refrigerant which has flowed into the outdoor unit 1 passes through the check valve 13c, and is sucked into the compressor 10 again via the first refrigerant flow switching device 11 and the accumulator 19.
  • the heat medium has been used for the heating operation, and as described above, the heat capacity is secured by temporarily increasing the temperature of the heat medium at the intermediate heat exchanger 25 before execution of the defrosting operation mode. Therefore, the heat medium maintains high temperature. Thus, even in the defrosting operation mode, a high-temperature heat medium may be conveyed to the use-side heat exchanger 35, that is, the heating operation may continue to be performed in the indoor unit 3.
  • each of the second heat medium flow switching devices 33 that are connected to the corresponding indoor units 3 is set to have an intermediate opening degree.
  • the heat medium flow control devices 34 are controlled such that the outlet temperature of the intermediate heat exchangers 25 and the outlet temperature of the use-side heat exchangers 35 are constant.
  • the first heat medium flow switching devices 32 are set to have the same opening degree of the second heat medium flow switching devices 33, and the heating operation by the conveyance of the heat medium may continue to be performed.
  • a high-temperature heat medium may flow into the use-side heat exchangers 35 during a defrosting operation, heat exchange with the outdoor air by the operation of the fans may be performed, and a heating operation by hot-air blowing may continue to be performed.
  • the air volume of the fan lower than the air volume (setting air volume) of the fan during a conventional heating operation
  • the heat capacity emitted to the indoor space by the use-side heat exchanger 35 may be limited, and the time during which the heat capacity of the heat medium is maintained may be extended.
  • the setting air volume which is the air volume of the fan during the conventional heating operation may be varied.
  • Fig. 10 is a graph illustrating an example of the relationship between the air volume of a fan for each temperature to which a heat medium may be reduced and the time during which the heat medium temperature may be maintained in the case where a heating operation continues to be performed with the air volume.
  • the emission amount and time of heat to the indoor space by blowing air from the fan may be estimated with respect to the heat capacity which may be held by the heat medium.
  • an appropriate air volume ratio and air volume maintenance time may be determined, and the heating operation mode may continue to be performed during the appropriate time at the appropriate temperature in the defrosting operation mode.
  • Fig. 11 is a refrigerant circuit diagram illustrating the flow of refrigerant and the flow of a heat medium in the "second bypass defrosting operation mode" of the air-conditioning apparatus 100.
  • the "second bypass defrosting operation mode” will be explained.
  • pipes indicated by thick lines represent pipes through which a heat-source-side refrigerant circulates.
  • solid arrows represent the flow direction of a heat-source-side cooling, and broken arrows represent the flow direction of a heat medium.
  • the "second bypass defrosting operation mode” is executed during the execution of the "second heat recovery defrosting operation mode" by being switched according to a change in the setting temperature.
  • the first refrigerant flow switching device 11 is switched to cause a heat-source-side refrigerant discharged from the compressor 10 to flow into the heat-source-side heat exchanger 12.
  • the pump 31a and the pump 31b are driven and the heat medium flow control devices 34a to 34d are opened, so that a heat medium may circulate between each of the intermediate heat exchanger 25a and the intermediate heat exchanger 25b and the use-side heat exchangers 35a to 35d.
  • the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b maintain a state being switched to the side of cooling operation, the opening and closing device 27 is opened, and the opening and closing device 29 is opened.
  • the expansion device 26a is controlled such that the refrigerant at the outlet of the intermediate heat exchanger 25a becomes a gas state, and the expansion device 26b is fully closed.
  • a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant, and is discharged.
  • the high-temperature and high-pressure gas refrigerant which has been discharged from the compressor 10 passes via the first refrigerant flow switching device 11, and flows into the heat-source-side heat exchanger 12.
  • the refrigerant that has flowed into the heat-source-side heat exchanger 12 exchanges heat with a frosting part on the heat-source-side heat exchanger 12.
  • the frosting part on the heat-source-side heat exchanger 12 is melted by the high-temperature, high-pressure refrigerant.
  • the low-temperature and high-pressure refrigerant that has exchanged heat with the frosting part on the heat-source-side heat exchanger 12 passes through the check valve 13a, and then flows out of the outdoor unit 1.
  • the low-temperature and high-pressure gas refrigerant which has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the relay unit 2.
  • the refrigerant which has flowed into the relay unit 2 passes through the opening and closing device 27, and is split.
  • the intermediate heat exchanger 25a due to the operation of the expansion device 26a, heat exchange with a heat medium continues to be performed to generate a low-temperature heat medium for cooling, and the generated low-temperature heat medium for cooling is supplied to the indoor unit 3. Meanwhile, no refrigerant is conveyed to the intermediate heat exchanger 25b, and heat exchange with a high-temperature heat medium which has been used for the heating operation is not performed.
  • the refrigerant flows that have passed through the intermediate heat exchanger 25a and the opening and closing device 29 are merged together.
  • the merged refrigerant flows out of the relay unit 2.
  • the refrigerant which has flowed out of the relay unit 2 passes through the refrigerant pipe 4, and flows into the outdoor unit.
  • the refrigerant which has flowed into the outdoor unit 1 passes through the check valve 13c, and is sucked into the compressor 10 again via the first refrigerant flow switching device 11 and the accumulator 19.
  • the heat medium whose temperature has been decreased at the intermediate heat exchanger 25a is pressurized by the pump 31a, passes through a corresponding one of the second heat medium flow switching devices 33a to 33d that corresponds to the indoor unit 3 in the cooling operation mode, and flows into the corresponding one of the use-side heat exchangers 35a to 35d.
  • the cooling operation continues to be performed by causing the heat medium which has been caused by the pump 31a to flow into the indoor unit 3 to be subjected to heat exchange with the indoor air of the indoor space 7 at the use-side heat exchanger 35.
  • the heat medium which has been subjected to heat exchange at the use-side heat exchanger 35 is conveyed into the relay unit 2 via the heat medium pipe 5 and the heat medium flow control device 34.
  • the flow rate of the heat medium which has been conveyed to each of the indoor units 3 is adjusted by the corresponding heat medium flow control device 34.
  • the heat medium which has flowed out of the heat medium flow control device 34 passes through the first heat medium flow switching device 32.
  • the heat medium that has passed through the first heat medium flow switching device 32 is subjected to heat exchange again with a heat-source-side refrigerant that has flowed into the intermediate heat exchanger 25a, and supplies the heat to the refrigerant side. After that, the heat medium is sucked again into the pump 31a.
  • the heat medium flowing into the intermediate heat exchanger 25b has been used for the heating operation, and as described above, the heat capacity is secured by temporarily increasing the temperature of the heat medium at the intermediate heat exchanger before execution of the defrosting operation mode. Therefore, the heat medium still has a high temperature.
  • a high-temperature heat medium may be conveyed to the use-side heat exchanger 35 by conveyance of the heat medium, that is, the heating operation may continue to be performed in the indoor unit 3.
  • each of the second heat medium flow switching devices 33 that are connected to the corresponding indoor units 3 is directed toward the intermediate heat exchanger 25b.
  • the heat medium flow control devices 34 after passing through the use-side heat exchangers 35 are controlled such that the outlet temperature of the intermediate heat exchanger 25b and the outlet temperature of the use-side heat exchanger are constant.
  • the first heat medium flow switching devices 32 are set to have the same opening degree of the second heat medium flow switching devices 33, and the heating operation by the conveyance of the heat medium may continue to be performed.
  • a high-temperature heat medium may flow into the use-side heat exchangers 35 during a defrosting operation, heat exchange with the outdoor air by the operation of the fans may be performed, and a heating operation by hot-air blowing may continue to be performed.
  • the heat capacity emitted to the indoor space by the use-side heat exchanger 35 may be limited, and the time during which the heat capacity of the heat medium is maintained may be extended.
  • the air-conditioning apparatus 100 exchanges heat between refrigerant and a heat medium via the relay unit 2 without causing the refrigerant to directly circulate in the indoor space in which the indoor units 3 are installed, and conveys the heat medium to the indoor units 3. Accordingly, a cooling operation and a heating operation can be achieved. Therefore, the air-conditioning apparatus 100 is able to avoid leakage of refrigerant into the indoor space. Furthermore, in the air-conditioning apparatus 100, refrigerant is conveyed from the outdoor unit 1 to the relay unit 2, and the relay unit 2 may thus be installed at an appropriate position. Therefore, the conveyance distance of a heat medium may be shortened, and the motive power of the pump 31a and the pump 31b may be reduced. Consequently, energy saving can be attained.
  • the air-conditioning apparatus 100 has a defrosting operation mode for removing frost on the heat-source-side heat exchanger 12 of the outdoor unit 1 based on detection of the evaporating temperature or the like.
  • this defrosting operation mode refrigerant which has been subjected to heat exchange by defrosting and whose temperature has been reduced is conveyed to the indoor units 3 during a heating operation.
  • the refrigerant is subjected to heat exchange with a heat medium whose temperature has been increased to a high temperature immediately before a defrosting operation, and is conveyed to the outdoor unit 1.
  • the air-conditioning apparatus 100 is able to continue an appropriate heating operation. Furthermore, even when the indoor units 3 may take in the outdoor air, the air-conditioning apparatus 100 may exchange heat with a heat medium in the defrosting operation mode, and may continue to perform a heating operation, as described above.
  • the first heat medium flow switching devices 32 and the second heat medium flow switching devices 33 explained above in Embodiment may be devices which may switch a flow passage, such as a combination of three-way valves or the like which may switch three-way flow passages and opening and closing valves or the like which may open and close two-way flow passages. Furthermore, a combination of stepping-motor mixing valves or the like which may change the flow rate of three-way flow passages and electronic expansion valves or the like which may change the flow rate of two-way flow passages, or the like may be used as the first heat medium flow switching devices 32 and the second heat medium flow switching devices 33. In this case, water hammer caused by sudden opening and closing of a flow passage may be prevented.
  • the heat medium flow switching devices 34 may be configured as control valves having three-way flow passages and may be installed together with a bypass pipe for bypassing the use-side heat exchangers 35.
  • stepping-motor-driven devices which may control the flow rate of flowing in a flow passage may be used as the heat medium flow control devices 34.
  • the devices may be two-way valves or three-way valves whose one end is closed.
  • opening and closing valves or the like which open and close two-way flow passages may be used as the heat medium flow control devices 34, and the average flow rate may be controlled by repeatedly turning on and off.
  • the second refrigerant flow switching devices 28 are not limited to this.
  • the second refrigerant flow switching devices 28 may be configured such that refrigerant flows in the same manner by using a plurality of two-phase flow passage switching valves or three-way flow passage switching valves.
  • heat medium flow control devices 34 are built in the relay unit 2
  • the heat medium flow control devices 34 are not necessarily built in the relay unit 2.
  • the heat medium flow control devices 34 may be built in the indoor units 3 or may be configured separately from the relay unit 2 and the indoor units 3.
  • a heat medium for example, brine (antifreeze), water, a liquid mixture of brine and water, a liquid mixture of water and an additive having high anticorrosion effect, or the like may be used. Therefore, in the air-conditioning apparatus 100, even if a heat medium is leaked into the indoor space 7 via the indoor units 3, the use of a heat medium with a high safety contributes to an improvement in the safety.
  • the air-conditioning apparatus 100 includes the accumulator 19
  • the accumulator 19 is not necessarily provided.
  • blower devices are attached to the heat-source-side heat exchanger 12 and the use-side heat exchangers 35, and blowing air often prompts condensation and evaporation.
  • the configuration is not limited to this.
  • panel heaters or the like which utilize radiation may be used as the use-side heat exchangers 35.
  • Devices of a water-cooled type for moving heat by using water or antifreeze may be used as the heat-source-side heat exchanger 12. That is, devices of any type may be used as the heat-source-side heat exchanger 12 and the use-side heat exchangers 35 as long as they have a structure which may transfer heat or receive heat.
  • the number of use-side heat exchangers 35 is not particularly limited. Furthermore, although the case where the two intermediate heat exchanger 25a and the intermediate heat exchanger 25b are provided is explained as an example, obviously, the number of intermediate heat exchangers is not limited to this. Any number of intermediate heat exchangers may be installed as long as the intermediate heat exchangers are able to cool or/and heat a heat medium. Furthermore, each of the number of pumps 31a and the number of pumps 31b is not necessarily one. A plurality of compact pumps may be connected in parallel to one another.

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Claims (7)

  1. Klimaanlage (100), umfassend:
    einen Kältemittelzirkulationskreislauf, um darin ein wärmequellenseitiges Kältemittel zu zirkulieren, wobei der Kältemittelzirkulationskreislauf einen Verdichter (10), einen wärmequellenseitigen Wärmetauscher (12), eine Vielzahl von Expansionseinrichtungen (26), kältemittelseitige Strömungsdurchgänge einer Vielzahl von Zwischenwärmetauschern (25) und eine Vielzahl von Kältemittelströmungsschalteinrichtungen (28), um einen Kältemittelzirkulationsdurchgang zu schalten, durch Kältemittelleitungen (4) verbindet;
    einen Wärmemediumzirkulationskreislauf, um darin ein Wärmemedium zu zirkulieren, wobei der Wärmemediumkreislauf eine Vielzahl von Wärmemediumbeförderungseinrichtungen (31), die in Verbindung mit der Vielzahl von Zwischenwärmetauschern (25) vorgesehen sind, eine Vielzahl von nutzungsseitigen Wärmetauschern (35), und wärmemediumseitige Strömungsdurchgänge für die Vielzahl von Zwischenwärmetauschern (25) durch Wärmemediumbeförderungsleitungen (5) verbindet; und
    eine Umgehungsleitung (20), die installiert ist, um durch Umgehen zumindest der Zwischenwärmetauscher (25) das wärmequellenseitige Kältemittel zu dem Verdichter (10) zurückzuführen,
    wobei die Vielzahl von Zwischenwärmetauschern (25) Wärme zwischen dem wärmequellenseitigen Kältemittel und dem Wärmemedium austauschen,
    dadurch gekennzeichnet, dass die Klimaanlage ferner umfasst
    eine Steuerungseinheit (50), die eingerichtet ist, die Klimaanlage (100) zu steuern, um auszuführen
    einen Erwärmungsbetriebsmodus, bei dem die Kältemittelströmungsschalteinrichtungen (28) zu einer Seite eines Erwärmungsbetriebs geschaltet werden, das Wärmemedium durch zumindest einen der Zwischenwärmetauscher (25) erwärmt wird, zumindest eine der Wärmemediumbeförderungseinrichtungen (31) betrieben wird, und das erwärmte Wärmemedium zumindest einem der nutzungsseitigen Wärmetauscher (35) zugeführt wird,
    einen Wärmerückgewinnung-Entfrostungsbetriebsmodus, bei dem um den wärmequellenseitigen Wärmetauscher (12) herum gebildeter Frost geschmolzen wird, durch Schalten der Kältemittelströmungsschalteinrichtungen (28) während des Erwärmungsbetriebs zu einer Seite eines Kühlungsbetriebs, Betreiben zumindest einer der Wärmemediumbeförderungseinrichtungen (31), und Veranlassen des wärmequellenseitigen Kältemittels, Wärme des Wärmemediums durch zumindest einen der Zwischenwärmetauscher (25) zu empfangen, und
    einen Umgehung-Entfrostungsbetriebsmodus, bei dem um den wärmequellenseitigen Wärmetauscher (12) herum gebildeter Frost geschmolzen wird, durch Schalten der Kältemittelströmungsschalteinrichtungen (28) während des Erwärmungsbetriebs zu der Seite eines Kühlungsbetriebs und Veranlassen eines Teils oder des gesamten wärmequellenseitigen Kältemittels, zu der Umgehungsleitung (20) zu strömen,
    wobei der Erwärmungsbetriebsmodus aufweist
    einen Erwärmungshauptbetriebsmodus, bei dem die Kältemittelströmungsschalteinrichtungen (28) zu der Seite eines Erwärmungsbetriebs geschaltet werden, das Wärmemedium durch zumindest einen der Zwischenwärmetauscher (25) erwärmt wird, und das Wärmemedium durch den Rest der Zwischenwärmetauscher (25) gekühlt wird,
    der Wärmerückgewinnung-Entfrostungsbetriebsmodus aufweist
    einen Modus, bei dem um den wärmequellenseitigen Wärmetauscher (12) herum gebildeter Frost geschmolzen wird, durch Schalten der Kältemittelströmungsschalteinrichtungen (28) zu einer Seite eines Kühlungsbetriebs, bei dem das kalte Wärmemedium veranlasst wird zu allen der Zwischenwärmetauscher (25) zu strömen, und bei dem das wärmequellenseitige Kältemittel veranlasst wird, im Wärmemedium gehaltene Wärme durch den zumindest einen der Zwischenwärmetauscher (25), die während des Erwärmungshauptbetriebsmodus Erwärmung ausgeführt haben, zu empfangen, während der zumindest eine der Zwischenwärmetauscher (25), der während des Erwärmungshauptbetriebsmodus Kühlung durchgeführt hat, veranlasst wird, weiter zu kühlen, und wenn die Klimaanlage (100) von dem Erwärmungshauptbetriebsmodus auf den Wärmerückgewinnung-Entfrostungsbetriebsmodus geschaltet wird, um Entfrostung durchzuführen, jede der Expansionseinrichtungen (26), die dem zumindest einen der Zwischenwärmetauscher (25) zugehörig sind, die während des Erwärmungshauptbetriebsmodus Erwärmung ausgeführt haben, vollständig geöffnet wird, und
    der Umgehung-Entfrostungsbetriebsmodus aufweist
    Schmelzen von um den wärmequellenseitigen Wärmetauscher (12) herum gebildetem Frost, durch Schalten der Kältemittelströmungsschalteinrichtungen (28) zu der Seite eines Kühlungsbetriebs, Veranlassen des kalten Kältemittels, zu zumindest einem der Zwischenwärmetauscher (25) zu strömen, Veranlassen eines Teils des Kältemittels, zu der Umgehungsleitung (20) zu strömen, während der Zwischenwärmetauscher (25), der während des Erwärmungshauptbetriebsmodus Kühlung durchgeführt hat, veranlasst wird, weiter zu kühlen, und Durchführen von Entfrostung durch Schalten auf den Umgehung-Entfrostungsbetriebsmodus aus dem Wärmerückgewinnung-Entfrostungsbetriebsmodus, und
    wobei bei dem Umgehung-Entfrostungsbetriebsmodus
    der Erwärmungsbetrieb weiterhin durchgeführt wird, durch Verwenden einer Wärmekapazität des Wärmemediums, das für den Erwärmungsbetrieb verwendet wurde, und
    beim Weiterführen des Erwärmungsbetriebsmodus
    eine Menge an Luft, die zu einem der nutzungsseitigen Wärmetauscher (35), der weiterhin den Erwärmungsbetrieb durchführt, geblasen wird, auf weniger als ein Einstellungsluftvolumen reduziert wird.
  2. Klimaanlage (100) nach Anspruch 1,
    wobei im Wärmerückgewinnung-Entfrostungsbetriebsmodus
    zumindest einer der Zwischenwärmetauscher (25) zum Veranlassen des wärmequellenseitigen Kältemittels, Wärme des Wärmemediums zu empfangen,
    gleich ist wie der zumindest eine der Zwischenwärmetauscher (25), der das Wärmemedium vor Ausführung des Wärmerückgewinnung-Entfrostungsbetriebsmodus erwärmt hat.
  3. Klimaanlage (100) nach Anspruch 1 oder 2, ferner umfassend:
    einen Wärmemedium-Temperatursensor (40), der an irgendeiner Position eines Strömungsdurchgangs auf einer Auslassseite des Wärmemediums des Zwischenwärmetauschers (25) vorgesehen ist,
    wobei der Wärmerückgewinnung-Entfrostungsbetriebsmodus ausgeführt wird, wenn eine durch den Wärmemedium-Temperatursensor (40) erfasste Temperatur des Wärmemediums höher ist als eine Temperatureinstellung, und
    wobei der Umgehung-Entfrostungsbetriebsmodus ausgeführt wird, wenn die durch den Wärmemedium-Temperatursensor (40) erfasste Temperatur des Wärmemediums niedriger ist als die Temperatureinstellung.
  4. Klimaanlage (100) nach Anspruch 3, ferner umfassend:
    einen nutzungsseitigen Lufttemperatursensor, der eine Temperatur von durch die nutzungsseitigen Wärmetauscher (35) strömender Luft erfasst,
    wobei die Temperatureinstellung
    gleich ist wie oder höher ist als die durch den nutzungsseitigen Lufttemperatursensor erfasste Temperatur.
  5. Klimaanlage (100) nach einem der Ansprüche 1 bis 4, wobei im Wärmerückgewinnung-Entfrostungsbetriebsmodus
    eine Gebläseeinrichtung, die Luft zu zumindest einem der nutzungsseitigen Wärmetauscher (35) bläst, der einen Erwärmungsbetrieb vor Beginn eines Entfrostungsbetriebs ausgeführt hat, angehalten wird, und
    eine Gebläseeinrichtung, die Luft zu zumindest einem der nutzungsseitigen Wärmetauscher (35) bläst, der einen Kühlungsbetrieb vor Beginn des Entfrostungsbetriebs ausgeführt hat, betrieben wird.
  6. Klimaanlage (100) nach einem der Ansprüche 1 bis 5, ferner umfassend:
    eine Vielzahl von Inneneinheiten (3), die jeden der Vielzahl von nutzungsseitigen Wärmetauschern (35) beherbergen;
    zumindest eine Außeneinheit (1), die den Verdichter (10) und den wärmequellenseitigen Wärmetauscher (12) beherbergt; und
    zumindest eine Relaiseinheit (2), die die Vielzahl von Zwischenwärmetauschern (25), die Vielzahl von Expansionseinrichtungen (26), die Vielzahl von Wärmemediumbeförderungseinrichtungen (31) und die Vielzahl von Kältemittelströmungsschalteinrichtungen (28) beherbergt,
    wobei die Inneneinheiten (3), die Außeneinheit (1) und die Relaiseinheit (2) eingerichtet sind, unabhängig voneinander ausgebildet zu sein und an voneinander getrennten Positionen installiert zu sein.
  7. Klimaanlage (100) nach Anspruch 1,
    wobei selbst dann, wenn Luft unter Verwendung von Außenluft, die zum Zwecke der Belüftung angesaugt wird, geblasen wird, warme Luft durch Durchführen eines Erwärmungsbetriebs unter Verwendung des Wärmemediums zugeführt werden kann.
EP13875678.8A 2013-02-25 2013-02-25 Klimaanlage Active EP2960602B1 (de)

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Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6609417B2 (ja) * 2015-04-03 2019-11-20 日立ジョンソンコントロールズ空調株式会社 空気調和機
JP6910210B2 (ja) * 2017-02-03 2021-07-28 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 空気調和装置
WO2019146070A1 (ja) * 2018-01-26 2019-08-01 三菱電機株式会社 冷凍サイクル装置
US11397035B2 (en) * 2018-07-20 2022-07-26 Mitsubishi Electric Corporation Controller of air conditioning apparatus, outdoor unit, relay unit, heat source unit, and air conditioning apparatus
US11802702B2 (en) * 2019-02-05 2023-10-31 Mitsubishi Electric Corporation Controller of air conditioning apparatus, outdoor unit, relay unit, heat source unit, and air conditioning apparatus
KR20200114123A (ko) * 2019-03-27 2020-10-07 엘지전자 주식회사 공기조화 장치
KR20200121200A (ko) 2019-04-15 2020-10-23 엘지전자 주식회사 공기조화 장치
CN113661364B (zh) * 2019-04-18 2023-03-10 三菱电机株式会社 空气调节装置的控制装置、室外机、中继机、热源机以及空气调节装置
CN112443934B (zh) * 2019-09-05 2021-11-02 青岛海尔空调电子有限公司 全热回收融霜控制方法、控制系统和空气调节装置
WO2021090810A1 (ja) * 2019-11-05 2021-05-14 ダイキン工業株式会社 空調室内機及び空気調和装置
KR20210096520A (ko) 2020-01-28 2021-08-05 엘지전자 주식회사 공기 조화 장치
CN112594871B (zh) * 2020-12-31 2022-02-08 广东积微科技有限公司 一种具有双四通阀多功能多联机系统的化霜控制方法
CN113685969B (zh) * 2021-07-26 2023-03-21 重庆海尔空调器有限公司 用于控制空调除霜的方法及装置、空调
CN113685970B (zh) * 2021-07-26 2023-02-17 重庆海尔空调器有限公司 用于控制空调除霜的方法及装置、空调
WO2024079874A1 (ja) * 2022-10-14 2024-04-18 三菱電機株式会社 空気調和装置

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05280818A (ja) * 1992-04-01 1993-10-29 Matsushita Refrig Co Ltd 多室冷暖房装置
BR0007811B1 (pt) * 1999-01-12 2009-01-13 sistema de compressço a vapor e mÉtodo para operar o sistema.
JP2001289465A (ja) 2000-04-11 2001-10-19 Daikin Ind Ltd 空気調和装置
JP4123829B2 (ja) * 2002-05-28 2008-07-23 三菱電機株式会社 冷凍サイクル装置
JP2005140444A (ja) 2003-11-07 2005-06-02 Matsushita Electric Ind Co Ltd 空気調和機およびその制御方法
US7340910B2 (en) * 2004-06-02 2008-03-11 Thompson Thomas W System and method of increasing efficiency of heat pumps
JP2007232303A (ja) * 2006-03-02 2007-09-13 Toyox Co Ltd 室内冷暖房換気システム
JP2008224189A (ja) * 2007-03-15 2008-09-25 Aisin Seiki Co Ltd 冷凍サイクル装置
EP2309199B1 (de) * 2008-10-29 2021-08-18 Mitsubishi Electric Corporation Klimaanlage
JP5387235B2 (ja) * 2009-08-28 2014-01-15 パナソニック株式会社 ヒートポンプ式温水暖房装置
JP5523470B2 (ja) * 2009-10-27 2014-06-18 三菱電機株式会社 空気調和装置
EP2535652B1 (de) * 2010-02-10 2023-08-16 Mitsubishi Electric Corporation Klimaanlage
EP2650621B1 (de) * 2010-12-09 2019-10-09 Mitsubishi Electric Corporation Klimaanlage
AU2011358038B2 (en) * 2011-01-31 2015-01-22 Mitsubishi Electric Corporation Air-conditioning apparatus
WO2013008278A1 (ja) * 2011-07-14 2013-01-17 三菱電機株式会社 空気調和装置

Non-Patent Citations (1)

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

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JPWO2014128970A1 (ja) 2017-02-02
JP6095764B2 (ja) 2017-03-15
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WO2014128970A1 (ja) 2014-08-28
CN105074359A (zh) 2015-11-18
US20150369498A1 (en) 2015-12-24

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