EP2584285B1 - Dispositif de climatisation à réfrigération - Google Patents

Dispositif de climatisation à réfrigération Download PDF

Info

Publication number
EP2584285B1
EP2584285B1 EP10853187.2A EP10853187A EP2584285B1 EP 2584285 B1 EP2584285 B1 EP 2584285B1 EP 10853187 A EP10853187 A EP 10853187A EP 2584285 B1 EP2584285 B1 EP 2584285B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
refrigeration
air
heat exchanger
conditioning
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.)
Not-in-force
Application number
EP10853187.2A
Other languages
German (de)
English (en)
Other versions
EP2584285A4 (fr
EP2584285A1 (fr
Inventor
Tsuyoshi Kubota
Hirofumi Koge
Koji Azuma
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP2584285A1 publication Critical patent/EP2584285A1/fr
Publication of EP2584285A4 publication Critical patent/EP2584285A4/fr
Application granted granted Critical
Publication of EP2584285B1 publication Critical patent/EP2584285B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—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
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • the present invention relates to a refrigerating and air-conditioning apparatus integrating an air-conditioning apparatus and a refrigeration apparatus and including a heat pump cycle, and in particular, relates to a refrigerating and air-conditioning apparatus that is devised to achieve stable supply of heat source throughout the year.
  • An air-conditioning and refrigeration apparatus comprising an air-conditioning system unit including an air-conditioning compressor, a heat-source side heat exchanger, and a use-side heat exchanger in which the an air-conditioned room is air-conditioned by the use-side heat exchanger; a cooling system unit including a cooling compressor, a condenser, and an evaporator in which a cooling and storing facility located in the air-conditioned room is cooled by the evaporator; and a cascade heat exchanger in which an air-conditioning refrigerant on a low-pressure side of the air-conditioning system unit and a cooling refrigerant on a high-pressure side of the refrigeration system unit is supplied to the cascade heat exchanger so as to cause the air-conditioning refrigerant to supercool the cooling refrigerant.
  • the air-conditioning system unit includes remote control means that issues instructions including start/stop instructions, wherein, the air-conditioning and refrigeration apparatus includes prohibiting means that prohibits, when the cooling compressor of the cooling system unit is operated, at least instructions other than the operating/stopping instructions out of the instructions issued from the remote control means" (see, for example, Patent Literature 1).
  • a refrigeration system comprising an air-conditioning refrigerant circuit formed of a compressor, a heat-source side heat exchanger, a pressure reducing device, and a use-side heat exchanger; a cooling and storing facility refrigerant circuit formed of a compressor, a condenser, a pressure reducing device, and an evaporator; and a cascade heat exchanger and a supercooling heat exchanger that cause heat to be exchanged between a low-pressure side of the air-conditioning refrigerant circuit and a high-pressure side of the cooling and storing facility refrigerant circuit, wherein, when a heating operation of the air-conditioning refrigerant circuit is performed, the high-pressure side refrigerant of the cooling and storing facility refrigerant circuit is caused to flow into the supercooling heat exchanger through the cascade heat exchanger and the condenser (see, for example, Patent Literature 2).
  • An object of the present invention is to provide a refrigerating and air-conditioning apparatus that is capable of simultaneously processing an air-conditioning load, such as a cooling load and a heating load, and a cold-storage/refrigeration load and that is capable of supplying a stable heat source throughout the year.
  • an air-conditioning load such as a cooling load and a heating load
  • a cold-storage/refrigeration load and that is capable of supplying a stable heat source throughout the year.
  • a refrigerating and air-conditioning apparatus has the features of claim 1.
  • an air-conditioning load and a cold-storage/refrigeration load can be simultaneously processed, and a stable heat source can be supplied throughout the year.
  • Fig. 1 is a refrigerant circuit diagram illustrating an example of a refrigerant circuit configuration of a refrigerating and air-conditioning apparatus 100.
  • the refrigerant circuit configuration and operation of the refrigerating and air-conditioning apparatus 100 are described with reference to Fig. 1 .
  • the refrigerating and air-conditioning apparatus 100 recovers heat during simultaneous cooling and heating operation.
  • the refrigerating and air-conditioning apparatus 100 is installed in an office building, an apartment, a hotel, or the like.
  • the refrigerating and air-conditioning apparatus 100 uses refrigeration cycles, in which refrigerants are circulated, so as to permit an air conditioning load and a cold-storage/refrigeration load to be simultaneously supplied.
  • the relationships among the sizes of components may differ from the actual relationships among the sizes of the components.
  • flows of refrigerants in a heating main operation performed by the refrigerating and air-conditioning apparatus 100 are illustrated.
  • the refrigerating and air-conditioning apparatus 100 has at least an air-conditioning refrigeration cycle 1 and a cold-storage/refrigeration refrigeration cycle 2.
  • the air-conditioning refrigeration cycle 1 and the cold-storage/refrigeration refrigeration cycle 2 are configured such that, a refrigerant-refrigerant heat exchanger 131 exchanges heat between a refrigerant of the air-conditioning refrigeration cycle 1 and a refrigerant of the cold-storage/refrigeration refrigeration cycle 2 without the refrigerants being mixed together.
  • the refrigerant circulated in the air-conditioning refrigeration cycle 1 is referred to as a primary-side refrigerant
  • the refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2 is referred to as a secondary-side refrigerant.
  • cold-storage/refrigeration the term means cold storage and/or refrigeration.
  • the air-conditioning refrigeration cycle 1 includes a heat source unit A, indoor units B (referred to as cooling indoor units B hereafter) that bears, for example, a cooling load, indoor units C (referred to as heating indoor units C hereafter) that bears, for example, a heating load, a cold-storage/refrigeration booster unit D (in particular, a primary side of the refrigerant-refrigerant heat exchanger 131) that serves as a heat source for the cold-storage/refrigeration refrigeration cycle 2, and a relay unit E.
  • the indoor units B are described as cooling indoor units and the indoor units C are described as heating indoor units, these are only examples of the functions of the indoor units B and the indoor units C.
  • the indoor units B may bear the heating load and the indoor units C may bear the cooling load. Note that when simply referred to as "indoor units", both indoor units B and indoor units C are included
  • the cooling indoor units B, the heating indoor units C, and the air-conditioning refrigeration cycle 1 side of the cold-storage/refrigeration booster unit D are connected in parallel to the heat source unit A through the relay unit E.
  • the relay unit E is disposed between the heat source unit A and the cooling indoor units B, the heating indoor units C, and the air-conditioning refrigeration cycle 1 side of the cold-storage/refrigeration booster unit D.
  • the relay unit E switches the flow of the primary-side refrigerant, thereby allowing the cooling indoor units B, heating indoor units C, and the cold-storage/refrigeration booster unit D to perform their respective functions.
  • the air-conditioning refrigeration cycle 1 side of the cold-storage/refrigeration booster unit D is referred to as a primary side of the cold-storage/refrigeration booster unit D
  • the cold-storage/refrigeration refrigeration cycle 2 side of the cold-storage/refrigeration booster unit D is referred to as a secondary side of the cold-storage/refrigeration booster unit D.
  • the heat source unit A supplies heating energy or cooling energy to the cooling indoor units B, the heating indoor units C, and the primary side of the cold-storage/refrigeration booster unit D through the relay unit E.
  • An air-conditioning compressor 101, a four-way valve 102 serving as a flow switching means, an outdoor heat exchanger (a heat-source side heat exchanger) 103, and an accumulator 104 are connected in series by pipes and are disposed in the heat source unit A.
  • a fan or other air-sending devices which supplies air to the outdoor heat exchanger 103, be provided at a position close to the outdoor heat exchanger 103.
  • the air-conditioning compressor 101 suctions and compresses the primary-side refrigerant so as to cause the primary-side refrigerant to enter a high-temperature high-pressure state.
  • the four-way valve 102 switches the flow of the primary-side refrigerant.
  • the outdoor heat exchanger 103 which functions as an evaporator or a radiator (condenser), causes heat to be exchanged between air supplied from the air-sending device (not shown) and the primary-side refrigerant, thereby evaporating and gasifying the primary-side refrigerant or condensing and liquefying the primary-side refrigerant.
  • the accumulator 104 is disposed on a suction side of the air-conditioning compressor 101 and stores the excessive primary-side refrigerant. It is sufficient that the accumulator 104 be a container in which the excessive primary-side refrigerant can be stored.
  • the heat source unit A includes a check valve 105a that allows the primary-side refrigerant in a high-pressure side connection pipe 106 between the outdoor heat exchanger 103 and the relay unit E to flow only in a fixed direction (a direction from the heat source unit A to the relay unit E) and a check valve 105b that allows the primary-side refrigerant in a low-pressure side connection pipe 107 between the four-way valve 102 and the relay unit E to flow only in a fixed direction (a direction from the relay unit E to the heat source unit A).
  • the high-pressure side connection pipe 106 and the low-pressure side connection pipe 107 are connected to each other by a first connection pipe 10, which connects a downstream side of the check valve 105a to a downstream side of the check valve 105b, and a second connection pipe 11, which an upstream side of the check valve 105a to an upstream side of the check valve 105b.
  • the first connection pipe 10 is provided with a check valve 105c, which allows the primary-side refrigerant to flow only in a direction from the low-pressure side connection pipe 107 to the high-pressure side connection pipe 106.
  • the second connection pipe 11 is provided with a check valve 105d, which allows the primary-side refrigerant to flow only in a direction from the low-pressure side connection pipe 107 to the high-pressure side connection pipe 106.
  • the indoor units receive cooling energy or heating energy supplied from the heat source unit A to cover the cooling load or the heating load.
  • An air-conditioning expansion means 117 and an indoor heat exchanger (use-side heat exchanger) 118 are connected in series and disposed in each indoor unit.
  • Fig. 1 an example is illustrated in which two cooling indoor units B and two heating indoor units C are connected.
  • fans or other air-sending devices which supply air to the indoor heat exchangers 118, be provided at positions close to the indoor heat exchangers 118.
  • pipes that connect the relay unit E to the indoor heat exchangers 118 are referred to as connection pipes 12, and pipes that connect the relay unit E to the air-conditioning expansion means 117 are referred to as connection pipes 13.
  • the air-conditioning expansion means 117 which have functions of pressure reducing valves and expansion valves, reduce the pressure of the primary-side refrigerant and expand the primary-side refrigerant. It is desirable that the air-conditioning expansion means 117 include means that can variably control its opening degrees, for example, precision flow rate control means using electronic expansion valves, or inexpensive refrigerant flow rate regulating means such as capillary tubes.
  • the indoor heat exchangers 118 function as radiators (condensers) or evaporators, cause heat to be exchanged between air supplied from the air-sending device (not shown) and the primary-side refrigerant, thereby condensing and liquefying the primary-side refrigerant or evaporating and gasifying the primary-side refrigerant.
  • the cold-storage/refrigeration booster unit D has a function of transferring cooling energy from the heat source unit A to the cold-storage/refrigeration refrigeration cycle 2 through the refrigerant-refrigerant heat exchanger 131.
  • An expansion means 119 and the refrigerant-refrigerant heat exchanger 131 are connected in series on the primary side of the cold-storage/refrigeration booster unit D.
  • the air-conditioning refrigeration cycle 1 and the cold-storage/refrigeration refrigeration cycle 2 are connected to each other in a cascade manner with the refrigerant-refrigerant heat exchanger 131. That is, the refrigerant-refrigerant heat exchanger 131 causes heat to be exchanged between the primary-side refrigerant and the secondary-side refrigerant.
  • the expansion means 119 which has the functions of a pressure reducing valve and an expansion valve, reduces the pressure of the primary-side refrigerant and expands the primary-side refrigerant. It is desirable that the expansion means 119 include means that can variably control its opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the refrigerant-refrigerant heat exchanger 131 which functions as a radiator (condenser) and an evaporator, causes heat to be exchanged between the secondary-side refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2 and the primary-side refrigerant circulated in the air-conditioning refrigeration cycle 1.
  • a pipe that connects the relay unit E to the refrigerant-refrigerant heat exchanger 131 is referred to as a connection pipe 14, and a connection pipe that connects the relay unit E to the expansion means 119 is referred to as a connection pipe 15.
  • the relay unit E connects the heat source unit A to use-side units (indoor units B, indoor units C, and cold-storage/refrigeration booster unit D) and alternatively opens or closes either of a valve means 109a and a valve means 109b of a first distribution section 109, thereby determining whether the indoor heat exchangers 118 are used as radiators or evaporators and whether the refrigerant-refrigerant heat exchanger 131 is used as a water cooling device or a water heating device.
  • the relay unit E includes at least a gas-liquid separator 108, the first distribution section 109, a second distribution section 110, a first internal heat exchanger 111, a first relay unit expansion means 112, a second internal heat exchanger 113, and a second relay unit expansion means 114.
  • connection pipes 12 and connection pipe 14 are each branched into two pipes.
  • One of the branched pipes (each of the connection pipes 12b and the connection pipe 14b) is connected to the low-pressure side connection pipe 107 and the other one of the branched pipes (each of the connection pipes 12a and the connection pipe 14a) is connected to a connection pipe (referred to as a connection pipe 16) that is connected to the gas-liquid separator 108.
  • the valve means 109a which are controlled to open or close so as to allow or not allow the refrigerant to be directed therethrough, are provided in the connection pipes 12a and the connection pipe 14a.
  • the valve means 109b which are controlled to open or close so as to allow or not allow the refrigerant to be directed therethrough, are provided in the connection pipes 12b and the connection pipe 14b.
  • connection pipes 13 and the connection pipe 15 are each branched into two pipes.
  • One of the branched pipes (each of the connection pipes 13a and the connection pipes 15a) are connected to one another in a first combining section 115 and the other one of the branched pipes (each of the connection pipes 13b and the connection pipes 15b) are connected to one another in a second combining section 116.
  • check valves 110a which allow the refrigerant to flow therethrough only in a single direction, are provided in the connection pipes 13a and the connection pipe 15a
  • check valves 110b which allow the refrigerant to flow therethrough only in a single direction
  • valve means such as solenoid valves may be used. By doing this, passages in the second distribution section 110 can be reliably switched.
  • the first combining section 115 connects the second distribution section 110 to the gas-liquid separator 108 through the first relay unit expansion means 112 and the first internal heat exchanger 111.
  • the second combining section 116 branches at a position between the second distribution section 110 and the second internal heat exchanger 113.
  • One of the branched second combining section 116 is connected to the first combining section 115 at a position between the second distribution section 110 and the first relay unit expansion means 112 through the second internal heat exchanger 113.
  • the other one of the branched second combining section 116 (a second combining section 116a) is connected to the low-pressure side connection pipe 107 through the second relay unit expansion means 114, the second internal heat exchanger 113, and the first internal heat exchanger 111.
  • the gas-liquid separator 108 separates the refrigerant into a gas refrigerant and a liquid refrigerant.
  • the gas-liquid separator 108 is provided in the high-pressure side connection pipe 106.
  • One end of the gas-liquid separator 108 is connected to the valve means 109a of the first distribution section 109 and another end of the gas-liquid separator 108 is connected to the second distribution section 110 through the first combining section 115.
  • the first distribution section 109 alternatively opens or closes either of the valve means 109a and the valve means 109b, thereby causing the refrigerant to flow into or flow out of the indoor heat exchangers 118 and the refrigerant-refrigerant heat exchanger 131.
  • the second distribution section 110 uses the check valves 110a and the check valves 110b so as to allow the refrigerant to flow through either of the check valves 110a and the check valves 110b.
  • the first internal heat exchanger 111 is provided in the first combining section 115 between the gas-liquid separator 108 and the first relay unit expansion means 112.
  • the first internal heat exchanger 111 causes heat to be exchanged between the refrigerant directed through the first combining section 115 and the refrigerant directed through the second combining section 116a, which is branched from the second combining section 116.
  • the first relay unit expansion means 112 is provided in the first combining section 115 between the first internal heat exchanger 111 and the second distribution section 110.
  • the first relay unit expansion means 112 reduces the pressure of the refrigerant and expands the refrigerant.
  • the first relay unit expansion means 112 include a means such as a means that can variably control an opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the second internal heat exchanger 113 is provided in the second combining section 116.
  • the second internal heat exchanger 113 causes heat to be exchanged between the refrigerant directed through the second combining section 116 and the refrigerant directed through the second combining section 116a branched from the second combining section 116.
  • the second relay unit expansion means 114 is provided in the second combining section 116 between the second internal heat exchanger 113 and the second distribution section 110.
  • the second relay unit expansion means 114 which functions as a pressure reducing valve and an expansion valve, reduces the pressure of the refrigerant and expands the refrigerant.
  • the second relay unit expansion means 114 include means that can variably control an opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the air-conditioning refrigeration cycle 1 is established by serially connecting the air-conditioning compressor 101, the four-way valve 102, the indoor heat exchangers 118, the air-conditioning expansion means 117, the outdoor heat exchanger 103, and the accumulator 104; by serially connecting the air-conditioning compressor 101, the four-way valve 102, the refrigerant-refrigerant heat exchanger 131, the expansion means 119, the outdoor heat exchanger 103, and the accumulator 104; by parallelly connecting the indoor heat exchangers 118 and the refrigerant-refrigerant heat exchanger 131 through the relay unit E; and by circulating the refrigerant through these components.
  • the air-conditioning compressor 101 may be any that is capable of compressing the suctioned refrigerant into a high-pressure state, and is not limited to a specific type of compressor.
  • the air-conditioning compressor 101 may use one of a variety of compressors such as reciprocating, rotary, scroll, and screw compressors.
  • the rotation speed of the air-conditioning compressor 101 may be variably controllable by an inverter or may be fixed.
  • the type of refrigerant circulated in the air-conditioning refrigeration cycle 1 is not particularly limited.
  • the refrigerant may be any one of the following: a natural refrigerant such as carbon dioxide (CO2), hydrocarbon, or helium, an alternative refrigerant without chlorine such as HFC410A, HFC407C, or HFC404A, and a fluorocarbon refrigerant used in existing products such as R22 or R134a.
  • a natural refrigerant such as carbon dioxide (CO2), hydrocarbon, or helium
  • an alternative refrigerant without chlorine such as HFC410A, HFC407C, or HFC404A
  • fluorocarbon refrigerant used in existing products such as R22 or R134a.
  • the refrigerating and air-conditioning apparatus 100 has a cooling only operation mode, in which all the indoor units perform cooling operation; a heating only operation mode, in which all the indoor units perform heating operation; a cooling main operation mode (see Fig. 2 ), in which heating and cooling are performed and the cooling load is greater; and a heating main operation mode, heating and cooling are performed and the heating load is greater.
  • the flow of the refrigerant is indicated by opening and closing states (hollow (open state) and solid (closed state)) of the check valves and the valve means.
  • the primary-side refrigerant the state of which has been turned into a high-temperature high-pressure gas by the air-conditioning compressor 101, is discharged from the air-conditioning compressor 101, flows through the four-way valve 102, is directed through the check valve 105c, is guided to the high-pressure side connection pipe 106, and flows into the gas-liquid separator 108 of the relay unit E in a superheated gas state.
  • the primary-side refrigerant in a superheated gas state having flowed into the gas-liquid separator 108 flows through the connection pipe 16 and is distributed to circuits where the valve means 109a of the first distribution section 109 are open, that is, to the heating indoor units C.
  • the primary-side refrigerant having flowed into the heating indoor units C transfers heat in the indoor heat exchangers 118 (that is, heats the indoor air). Then the pressure of the primary-side refrigerant is reduced by the air-conditioning expansion means 117, and the flows of the primary-side refrigerant are merged with each other in the first combining section 115.
  • part of the primary-side refrigerant in a superheated gas state having flowed into the gas-liquid separator 108 exchanges heat in the first internal heat exchanger 111 with the primary-side refrigerant, which has been expanded by the second relay unit expansion means 114 and has a low temperature and a low pressure, thereby becoming to have a degree of supercooling.
  • the part of the primary-side refrigerant passes through the first relay unit expansion means 112 and, in the first combining section 115, is merged with the primary-side refrigerant having been used for air-conditioning (the primary-side refrigerant that has flowed into the heating indoor units C and that has transferred heat in the indoor heat exchangers 118).
  • the part of the primary-side refrigerant in a superheated gas state passing through the first relay unit expansion means 112 may be completely shut off by completely closing the first relay unit expansion means 112.
  • the merged primary-side refrigerant exchanges heat in the second internal heat exchanger 113 with the primary-side refrigerant, which has been expanded by the second relay unit expansion means 114 and has a low temperature and a low pressure, thereby becoming to have a degree of supercooling.
  • This primary-side refrigerant is distributed to the second combining section 116 side and the second relay unit expansion means 114 side.
  • the primary-side refrigerant directed through the second combining section 116 is distributed to circuits where the valve means 109b are open, that is, to the cooling indoor units B and the primary side of the cold-storage/refrigeration booster unit D.
  • the primary-side refrigerant having flowed into the cooling indoor units B is expanded by the air-conditioning expansion means 117 so as to have a low temperature and a low pressure, evaporates in the indoor heat exchangers 118, and flows into the low-pressure side connection pipe 107 through the valve means 109b.
  • the primary-side refrigerant having flowed into the primary side of the cold-storage/refrigeration booster unit D is expanded by the expansion means 119 so as to have a low temperature and a low pressure, evaporates in the refrigerant-refrigerant heat exchanger 131, and flows into the low-pressure side connection pipe 107 through the valve means 109b.
  • the primary-side refrigerant having been directed through the second relay unit expansion means 114 exchanges heat in the second internal heat exchanger 113 and the first internal heat exchanger 111 to evaporate, and is, in the low-pressure side connection pipe 107, merged with the primary-side refrigerant that has flowed out from the cooling indoor units B and the primary side of the cold-storage/refrigeration booster unit D.
  • the primary-side refrigerant having been merged in the low-pressure side connection pipe 107 passes through the check valve 105d, is guided to the outdoor heat exchanger 103, in which the liquid refrigerant that is made to remain depending on the operation condition is made to evaporate, and returns to the air-conditioning compressor 101 through the four-way valve 102 and the accumulator 104.
  • the cold-storage/refrigeration refrigeration cycle 2 includes the cold-storage/refrigeration booster unit D (in particular, the secondary side of the refrigerant-refrigerant heat exchanger 131) and a cold-storage/refrigeration unit F. That is, the cold-storage/refrigeration refrigeration cycle 2 includes a refrigeration compressor 130 disposed in the cold-storage/refrigeration booster unit D, the refrigerant-refrigerant heat exchanger 131, refrigeration expansion means 132, and a refrigeration heat exchanger 133 disposed in the cold-storage/refrigeration unit F connected in series by pipes.
  • the cold-storage/refrigeration refrigeration cycle 2 is connected to the air-conditioning refrigeration cycle 1 through the refrigerant-refrigerant heat exchanger 131 disposed in the cold-storage/refrigeration booster unit D.
  • the cold-storage/refrigeration booster unit D transfers heating energy or cooling energy from the heat source unit A to the cold-storage/refrigeration refrigeration cycle 2 through the refrigerant-refrigerant heat exchanger 131.
  • the refrigeration compressor 130, the secondary side of the refrigerant-refrigerant heat exchanger 131, and the refrigeration expansion means 132 are connected in series on the secondary side of the cold-storage/refrigeration booster unit D.
  • the refrigeration compressor 130 suctions and compresses the secondary-side refrigerant so as to cause the secondary-side refrigerant to enter a high-temperature high-pressure state.
  • the rotation speed of the refrigeration compressor 130 may be variably controllable by an inverter or may be fixed.
  • the refrigeration compressor 130 may be any that is capable of compressing the suctioned secondary-side refrigerant into a high-pressure state, and is not limited to a specific type of compressor.
  • the refrigeration compressor 130 may use one of a variety of compressors such as reciprocating, rotary, scroll, and screw compressors.
  • the refrigerant-refrigerant heat exchanger 131 causes heat to be exchanged between the primary-side refrigerant circulated in the air-conditioning refrigeration cycle 1 and the secondary-side refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2.
  • the refrigeration expansion means 132 which has the functions of a pressure reducing valve and an expansion valve, reduces the pressure of the secondary-side refrigerant and expand the secondary-side refrigerant. It is desirable that the refrigeration expansion means 132 include means that can variably control an opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the type of the secondary-side refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2 is not particularly limited.
  • the secondary-side refrigerant may be, for example, any one of a natural refrigerant such as carbon dioxide, hydrocarbon, or helium; an alternative refrigerant without chlorine such as HFC410A, HFC407C, or HFC404A; and a fluorocarbon refrigerant used in existing products such as R22 or R134a.
  • the cold-storage/refrigeration unit F receives cooling energy supplied from the cold-storage/refrigeration booster unit D and covers the cold-storage/refrigeration load.
  • the refrigeration heat exchanger 133 is disposed in the cold-storage/refrigeration unit F.
  • the refrigeration heat exchanger 133 is provided between the refrigeration expansion means 132 and the refrigeration compressor 130 of the cold-storage/refrigeration booster unit D, functions as an evaporator, causes heat to be exchanged between air supplied from the air-sending device (not shown) and the secondary-side refrigerant, and evaporates and gasifies the secondary-side refrigerant.
  • a fan or other air-sending devices which supplies air to the refrigeration heat exchanger 133, be provided at a position close to the refrigeration heat exchanger 133.
  • the secondary-side refrigerant having flowed into the refrigerant-refrigerant heat exchanger 131 is cooled and condensed by the primary side circulated in the air-conditioning refrigeration cycle 1.
  • This secondary-side refrigerant is expanded by the refrigeration expansion means 132.
  • the expanded secondary-side refrigerant flows out of the cold-storage/refrigeration booster unit D and flows into the cold-storage/refrigeration unit F.
  • the secondary-side refrigerant having flowed into the cold-storage/refrigeration unit F receives heat from air supplied from the air-sending device (not shown) and evaporates in the refrigeration heat exchanger 133, and flows out of the cold-storage/refrigeration unit F.
  • the secondary-side refrigerant having flowed out of the cold-storage/refrigeration unit F flows into the secondary side of the cold-storage/refrigeration booster unit D and returns to the refrigeration compressor 130.
  • the refrigerating and air-conditioning apparatus 100 desirably includes sensors or the like that detect a discharge pressure and a suction pressure of the primary-side refrigerant, a discharge temperature and a suction temperature of the primary-side refrigerant, the temperature of the primary-side refrigerant flowing into and out of the outdoor heat exchanger 103, the temperature of outside air taken into the heat source unit A, the temperature of the primary-side refrigerant flowing into and out of the indoor heat exchangers 118, a discharge pressure and a suction pressure of the secondary-side refrigerant, a discharge temperature and a suction temperature of the secondary-side refrigerant, the temperature of the secondary-side refrigerant flowing into and out of the refrigeration heat exchanger 133, the temperature of outside air taken in the cold-storage/refrigeration unit F, and the temperatures of the primary-side refrigerant and the secondary-side refrigerant flowing into and out of the refrigerant-refrigerant heat exchange
  • controlling means that controls the operation of the refrigerating and air-conditioning apparatus 100 and used for control of the drive frequency of the air-conditioning compressor 101, switching of the four-way valve 102, opening and closing of the valve means 109a and the valve means 109b, the drive frequency of the refrigeration compressor 130, the opening degrees of various expansion devices, and the like.
  • the air-conditioning refrigeration cycle 1 and the cold-storage/refrigeration refrigeration cycle 2 have respective independent refrigerant circuit configurations (the air-conditioning refrigeration cycle 1 and the cold-storage/refrigeration refrigeration cycle 2).
  • the refrigerants circulated in the respective refrigerant circuits may be of the same type or of different types. That is, the refrigerants of the respective refrigerant circuits flow such that, in the refrigerant-refrigerant heat exchanger 131, heat is exchanged between the refrigerants while the refrigerants are not mixed with each other.
  • the excess refrigerant is stored in a liquid receiving unit (accumulator 104) in the air-conditioning refrigeration cycle 1
  • the accumulator 104 may be omitted in the case where the excess refrigerant is stored in the heat exchanger that functions as a radiator in the refrigeration cycle.
  • Fig. 1 an example in which two cooling indoor units B and two heating indoor units C are connected is illustrated. Alternatively, one or more cooling indoor units B and zero or one or more heating indoor units C may be connected.
  • one cold-storage/refrigeration booster unit D and one cold-storage/refrigeration unit F are connected, this does not limit the numbers of the cold-storage/refrigeration booster units D and the cold-storage/refrigeration units F to be connected.
  • two or more cold-storage/refrigeration booster units D may be connected, or two or more cold-storage/refrigeration units F may be connected.
  • Capacities of the disposed indoor units and the disposed cold-storage/refrigeration booster unit D may all be uniform, or may be varied from large to small capacities.
  • a cold storage or refrigeration load system is configured as a binary cycle.
  • a low temperature for example, -20°C
  • the refrigerating and air-conditioning apparatus 100 performs heating air-conditioning by reusing exhaust heat recovered in the cold-storage/refrigeration refrigeration cycle 2.
  • the system COP is significantly improved and energy is saved.
  • Fig. 2 is a refrigerant circuit diagram illustrating flows of the refrigerants in a cooling main operation of the refrigerating and air-conditioning apparatus 100 according to Embodiment 1.
  • the cooling main operation of the air-conditioning refrigeration cycle 1 performed by the refrigerating and air-conditioning apparatus 100 is described with reference to Fig. 2 .
  • the flow of the refrigerant is indicated by opening and closing states (hollow (open state) and solid (closed state)) of the check valves and valve means.
  • the primary-side refrigerant in a gaseous state is discharged from the air-conditioning compressor 101 and flows into the outdoor heat exchanger 103 through the four-way valve 102.
  • the primary-side refrigerant having flowed into the outdoor heat exchanger 103 transfers heat to air supplied to the outdoor heat exchanger 103 so as to be cooled down to about the ambient temperature.
  • This primary-side refrigerant flows out of the outdoor heat exchanger 103, is directed through the check valve 105a, is guided to the high-pressure side connection pipe 106, and flows into the gas-liquid separator 108 of the relay unit E.
  • the primary-side refrigerant having flowed into the gas-liquid separator 108 flows out of the gas-liquid separator 108 and flows into the first internal heat exchanger 111.
  • the primary-side refrigerant having flowed into the first internal heat exchanger 111 exchanges heat with the primary-side refrigerant, which has been expanded by the second relay unit expansion means 114 and has a low temperature and a low pressure, thereby becoming to have a degree of supercooling. Then the primary-side refrigerant passes through the first relay unit expansion means 112 and is merged with the primary-side refrigerant having been used for air-conditioning at the first combining section 115.
  • the merged primary-side refrigerant exchanges heat in the second internal heat exchanger 113 with the primary-side refrigerant, which has been expanded by the second relay unit expansion means 114 and has a low temperature and a low pressure, thereby further becoming to have a degree of supercooling. Then, the merged primary-side refrigerant is divided into the primary-side refrigerant that flows through the second combining section 116 and the primary-side refrigerant that flows through the second relay unit expansion means 114.
  • the primary-side refrigerant passing through the second combining section 116 is distributed to the circuits where the valve means 109b are open, that is, to the cooling indoor units B and the primary side of the cold-storage/refrigeration booster unit D.
  • the primary-side refrigerant having flowed into the cooling indoor units B is expanded by the air-conditioning expansion means 117 so as to have a low temperature and a low pressure, evaporates in the indoor heat exchangers 118, and flows into the low-pressure side connection pipe 107 through the valve means 109b.
  • the primary-side refrigerant having flowed into the primary side of the cold-storage/refrigeration booster unit D is expanded by the expansion means 119 so as to have a low temperature and a low pressure, evaporates in the refrigerant-refrigerant heat exchanger 131, and flows into the low-pressure side connection pipe 107 through the valve means 109b.
  • the primary-side refrigerant having been directed through the second relay unit expansion means 114 exchanges heat in the second internal heat exchanger 113 and the first internal heat exchanger 111 to evaporate, and is, in the low-pressure side connection pipe 107, merged with the primary-side refrigerant having flowed out from the cooling indoor units B and the primary side of the cold-storage/refrigeration booster unit D.
  • the primary-side refrigerant which has been separated by the gas-liquid separator 108 and is in a gaseous state, is distributed to the heating indoor unit C side through the valve means 109a.
  • the primary-side refrigerant having flowed into the heating indoor units C transfers heat in the indoor heat exchangers 118.
  • the pressure of the primary-side refrigerant is reduced by the air-conditioning expansion means 117, and flows of the primary-side refrigerant are merged with each other in the first combining section 115.
  • the primary-side refrigerant having been merged in the low-pressure side connection pipe 107 returns to the air-conditioning compressor 101 through the check valve 105b, the four-way valve 102, and the accumulator 104.
  • the flow of the secondary-side refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2 is similar to that in the heating main operation.
  • an optimum load-side unit can be selected in accordance with the air-conditioning load, the cold storage load, and the refrigeration load.
  • the refrigerating and air-conditioning apparatus 100 there is no need of separate new pipes provided from the heat source unit A to each of the load-side units and only the load-side units needs to be connected by pipes to the relay unit E. This can reduce the amount of used pipes.
  • an air-conditioning load and a cold-storage/refrigeration load can be simultaneously supplied using a binary refrigeration cycle.
  • Fig. 3 is a refrigerant circuit diagram illustrating an example of a refrigerant circuit configuration of a refrigerating and air-conditioning apparatus 100a according to Embodiment 2.
  • the configuration of the refrigerant circuit of the refrigerating and air-conditioning apparatus 100a that I one that recovers heat during simultaneous cooling and heating operation is described with reference to Fig. 3 .
  • the refrigerating and air-conditioning apparatus 100a is installed in an office building, an apartment, a hotel, or the like.
  • the refrigerating and air-conditioning apparatus 100a uses refrigeration cycles, in which refrigerants are circulated, so as to permit the air conditioning load and the cold-storage/refrigeration load to be simultaneously supplied.
  • Embodiment 2 points that are different from Embodiment 1 is mainly described, and the same components as those of Embodiment 1 are denoted by the same reference signs and description thereof is omitted.
  • the cold-storage/refrigeration booster unit D and the cold-storage/refrigeration unit F are separate housings and are connected to each other by pipes; however, in an exemplary configuration described in Embodiment 2, the cold-storage/refrigeration booster unit and the cold-storage/refrigeration unit are a single housing (a unit G illustrated in Fig. 3 ).
  • the cold-storage/refrigeration booster unit and the cold-storage/refrigeration unit are a single housing (a unit G illustrated in Fig. 3 ).
  • Fig. 4 is a refrigerant circuit diagram illustrating an example of a refrigerant circuit configuration of a refrigerating and air-conditioning apparatus 100b according to the present invention.
  • the configuration of the refrigerant circuit and operation of the refrigerating and air-conditioning apparatus 100b that recovers heat by simultaneous cooling and heating operation is described with reference to Fig. 4 .
  • the refrigerating and air-conditioning apparatus 100b is installed in an office building, an apartment, a hotel, or the like.
  • the refrigerating and air-conditioning apparatus 100b uses refrigeration cycles, in which refrigerants are circulated, so as to permit the air conditioning load, a hot-water load, and the cold-storage/refrigeration load to be simultaneously supplied.
  • Embodiment 3 points that are different from Embodiment 1 and Embodiment 2 are mainly described, and the same components as those of Embodiment 1 or Embodiment 2 are denoted by the same reference signs and description thereof is omitted.
  • the refrigerating and air-conditioning apparatus 100b according to Embodiment 3 has a configuration in which a hot-water supply system is added to the refrigerating and air-conditioning apparatus according to Embodiment 1 and 2. That is, the refrigerating and air-conditioning apparatus 100b not only has the air-conditioning refrigeration cycle 1 and the cold-storage/refrigeration refrigeration cycle 2 but also has a hot-water supply refrigeration cycle 3 and a hot-water load-side cycle 4.
  • the air-conditioning refrigeration cycle 1 and the hot-water supply refrigeration cycle 3 are formed such that, in a refrigerant-refrigerant heat exchanger 141, heat is exchanged between the refrigerant of the air-conditioning refrigeration cycle 1 and a refrigerant of the hot-water supply refrigeration cycle 3 while the refrigerant of the air-conditioning refrigeration cycle 1 and the refrigerant of the hot-water supply refrigeration cycle 3 are not mixed with each other.
  • the hot-water supply refrigeration cycle 3 and the hot-water load-side cycle 4 are formed such that, in a heat medium-refrigerant heat exchanger 143, heat is exchanged between the refrigerant of the hot-water supply refrigeration cycle 3 and a heat medium (for example, water, an anti-freeze solution, or the like) of the hot-water load-side cycle 4 while the refrigerant of the hot-water supply refrigeration cycle 3 and the heat medium of the hot-water load-side cycle 4 are not mixed with each other.
  • the refrigerant circulated in the hot-water supply refrigeration cycle 3 is referred to as a hot-water supply refrigerant.
  • the hot-water supply refrigeration cycle 3 includes a hot-water supply compressor 140 disposed in a hot-water supply booster unit H, the hot-water supply refrigerant side of the heat medium-refrigerant heat exchanger 143, a hot-water supply expansion means 142, and the hot-water supply refrigerant side of the refrigerant-refrigerant heat exchanger 141 that are connected in series by pipes.
  • the hot-water supply refrigeration cycle 3 supplies heating energy from the heat source unit A to a hot-water supply unit I through the refrigerant-refrigerant heat exchanger 141.
  • the hot-water supply booster unit H is disposed such that, as is the case with the indoor units or the cold-storage/refrigeration booster unit D, the hot-water supply booster unit H is connected in parallel to the heat source unit A.
  • the hot-water supply booster unit H performs its function when the flow of the primary-side refrigerant is switched by the relay unit E.
  • the hot-water load-side cycle 4 includes a water circulation pump 144 disposed in the hot-water supply unit I, the heat medium side of the heat medium-refrigerant heat exchanger 143, and a hot-water storage tank 145 that are connected in series by pipes.
  • the hot-water load-side cycle 4 boils water stored in the hot-water storage tank 145 using heating energy transferred through the heat medium-refrigerant heat exchanger 143 of the hot-water supply booster unit H.
  • the hot-water supply booster unit H transfers heating energy from the heat source unit A to the hot-water supply refrigeration cycle 3 through the refrigerant-refrigerant heat exchanger 141.
  • An expansion means 120 and the refrigerant-refrigerant heat exchanger 141 are connected in series on the primary side of the hot-water supply booster unit H.
  • the hot-water supply compressor 140, the hot-water supply refrigerant side of the heat medium-refrigerant heat exchanger 143, the hot-water supply expansion means 142, and the hot-water supply refrigerant side of the refrigerant-refrigerant heat exchanger 141 are connected in series.
  • the air-conditioning refrigeration cycle 1 and the hot-water supply refrigeration cycle 3 are connected to each other in a cascade manner with the refrigerant-refrigerant heat exchanger 141. That is, the refrigerant-refrigerant heat exchanger 141 causes heat to be exchanged between the primary-side refrigerant and the hot-water supply refrigerant.
  • the expansion means 120 which has functions of a pressure reducing valve and expansion valve, reduces the pressure of the primary-side refrigerant and expands the primary-side refrigerant. It is desirable that the expansion means 120 include a means such as a means that can variably control an opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the refrigerant-refrigerant heat exchanger 141 which functions as a radiator (condenser) or an evaporator, causes heat to be exchanged between the hot-water supply refrigerant circulated in the hot-water supply refrigeration cycle 3 and the primary-side refrigerant circulated in the air-conditioning refrigeration cycle 1.
  • a pipe that connects the relay unit E to the refrigerant-refrigerant heat exchanger 141 is referred to as the connection pipe 14a
  • a connection pipe that connects the relay unit E to the expansion means 120 is referred to as the connection pipe 15a.
  • the hot-water supply compressor 140 suctions and compresses the hot-water supply refrigerant so as to cause the hot-water supply refrigerant to enter a high-temperature high-pressure state.
  • the rotation speed of the hot-water supply compressor 140 may be variably controllable by an inverter or may be fixed.
  • the hot-water supply compressor 140 may be any that is capable of compressing the suctioned refrigerant into a high-pressure state, and is not limited to a specific type of compressor.
  • the hot-water supply compressor 140 may use one of a variety of compressors such as reciprocating, rotary, scroll, and screw compressors.
  • the heat medium-refrigerant heat exchanger 143 causes heat to be exchanged between the hot-water supply refrigerant circulated in the hot-water supply refrigeration cycle 3 and the heat medium circulated in the hot-water load-side cycle. That is, the hot-water supply refrigeration cycle 3 and the hot-water load-side cycle are connected to each other in a cascade manner through the heat medium-refrigerant heat exchanger 143.
  • the hot-water supply expansion means 142 which has the functions of a pressure reducing valve and an expansion valve, reduces the pressure of the hot-water supply refrigerant and expands the hot-water supply refrigerant.
  • the hot-water supply expansion means 142 include a means such as a means that can variably control an opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the type of the refrigerant circulated in the hot-water supply refrigeration cycle 3 is not particularly limited.
  • the refrigerant may be, for example, any one of a natural refrigerant such as carbon dioxide, hydrocarbon, or helium, an alternative refrigerant without chlorine such as HFC410A, HFC407C, or HFC404A, and a fluorocarbon refrigerant used in existing products such as R22 or R134a.
  • the hot-water supply unit I boils water using heating energy supplied from the hot-water supply booster unit H.
  • the water circulation pump 144, the heat medium side of the heat medium-refrigerant heat exchanger 143, and the hot-water storage tank 145 are connected in series in the hot-water supply unit I. That is, the hot-water supply unit I is established by the water circulation pump 144, the heat medium-refrigerant heat exchanger 143, and the hot-water storage tank 145 that are connected so as to form the hot-water load-side cycle 4, in which the heat medium is circulated.
  • the pipes of the hot-water load-side cycle 4 includes, for example, copper pipes, stainless pipes, steel pipes, polyvinyl chloride-based pipes, or the like.
  • the water circulation pump 144 suctions the water stored in the hot-water storage tank 145 and apply pressure to the water so as to circulate the water in the hot-water load-side cycle 4. It is desirable that the rotation speed of the water circulation pump 144 be controlled by, for example, an inverter. As described above, the heat medium-refrigerant heat exchanger 143 causes heat to be exchanged between the heat medium circulated in the hot-water load-side cycle 4 and the hot-water supply refrigerant circulated in the hot-water supply refrigeration cycle 3, Water heated by the heat medium-refrigerant heat exchanger 143 is stored in the hot-water storage tank 145.
  • the hot-water supply booster unit H and the cold-storage/refrigeration booster unit D are incorporated into a single system. This is expected to increase opportunities of loads for cooling (the cooling load and cold-storage/refrigeration load) and loads for heating (the heating load and hot-water load) being simultaneously used throughout the year, and accordingly, to increase energy saving effects due to heat recovery.
  • the heat source unit A, the indoor units, the cold-storage/refrigeration unit F, operation of the relay unit E, and the flow of the primary-side refrigerant of the refrigerating and air-conditioning apparatus 100b are similar to those in Embodiment 1 and Embodiment 2.
  • the flow of the primary-side refrigerant flowing from the relay unit E to the hot-water supply booster unit H is similar to the flow of the primary-side refrigerant flowing from the relay unit E to the heating indoor units C.
  • High-temperature refrigerant gas is directed through the valve means 109a, transfers heat in the refrigerant-refrigerant heat exchanger 141, passes through the expansion means 119, and is merged in the first combining section 115.
  • the hot-water supply refrigerant In the hot-water supply booster unit H, the hot-water supply refrigerant, the temperature and pressure of which have been increased by the hot-water supply compressor 140, is discharged from the hot-water supply compressor 140 and flows into the heat medium-refrigerant heat exchanger 143. In the heat medium-refrigerant heat exchanger 143, the hot-water supply refrigerant having flowed in transfers heat by heating the heat medium circulated in the hot-water load-side cycle 4. This hot-water supply refrigerant is expanded by the hot-water supply expansion means 142. The expanded hot-water supply refrigerant receives heat from the primary-side refrigerant of the air-conditioning refrigeration cycle 1 and evaporates in the refrigerant-refrigerant heat exchanger 141, and returns to the hot-water supply compressor 140.
  • the type of the secondary-side refrigerant circulated in the hot-water supply refrigeration cycle 3 is not particularly limited.
  • the secondary-side refrigerant may be, for example, any one of a natural refrigerant such as carbon dioxide, hydrocarbon, or helium, an alternative refrigerant without chlorine such as HFC410A, HFC407C, or HFC404A, and a fluorocarbon refrigerant used in existing products such as R22 or R134a.
  • the air-conditioning refrigeration cycle 1 and the hot-water supply refrigeration cycle 3 have respective independent refrigerant circuit configurations.
  • the refrigerants circulated in the respective refrigerant circuits may be of the same type or of different types.
  • the refrigerants of the respective refrigerant circuits flow such that, in the refrigerant-refrigerant heat exchanger 141, heat is exchanged between the refrigerants of the respective refrigerant circuits while the refrigerants are not mixed with each other.
  • a hot-water load system is configured as a binary cycle.
  • a high temperature for example, 80°C
  • a high temperature for example, condensing temperature of 85°C.
  • the hot water needs to be supplied using a boiler or the like.
  • the refrigerating and air-conditioning apparatus 100b heating energy that has been conventionally emitted to the atmosphere is recovered and reused for supplying hot water.
  • the system COP is significantly improved and energy is saved.
  • the water circulation pump 144 draws water, which is stored in the hot-water storage tank 145 and has a comparatively low temperature, from a bottom of the hot-water storage tank 145 and applies pressure to the water.
  • the water to which pressure is applied by the water circulation pump 144, flows into the heat medium-refrigerant heat exchanger 143 and receives heat in the heat medium-refrigerant heat exchanger 143 from the hot-water supply refrigerant circulated in the hot-water supply refrigeration cycle 3. That is, the water having flowed into the heat medium-refrigerant heat exchanger 143 is boiled by the hot-water supply refrigerant circulated in the hot-water supply refrigeration cycle 3, and the temperature of the water is increased.
  • the boiled water returns to an upper portion of the hot-water storage tank 145, in which the temperature is comparatively high, and is stored in the hot-water storage tank 145.
  • the accumulator 104 may be omitted in the case where the excess refrigerant is stored in the heat exchanger that functions as a radiator in the refrigeration cycle.
  • Fig. 4 an example in which two cooling indoor units B and two heating indoor units C are connected is illustrated. Alternatively, zero or three or more cooling indoor units B and zero or one or three or more heating indoor units C may be connected.
  • one hot-water supply booster unit H and one hot-water supply unit I are connected, this does not limit the numbers of the hot-water supply booster units H and the hot-water supply units I to be connected.
  • two or more hot-water supply booster units H may be connected, or two or more hot-water supply units I may be connected.
  • one cold-storage/refrigeration booster unit D and one cold-storage/refrigeration unit F are connected, this does not limit the numbers of the cold-storage/refrigeration booster units D and the cold-storage/refrigeration units F to be connected.
  • two or more cold-storage/refrigeration booster units D may be connected, or two or more cold-storage/refrigeration units F may be connected.
  • Capacities of the disposed indoor units and the booster units may all be uniform, or may be varied from large to small capacities.
  • Fig. 5 is a refrigerant circuit diagram illustrating an example of a refrigerant circuit configuration of a refrigerating and air-conditioning apparatus 100c according to Embodiment 4.
  • the refrigerant circuit configuration and operation of the refrigerating and air-conditioning apparatus 100c are described with reference to Fig. 5 .
  • the refrigerating and air-conditioning apparatus 100c is installed in an office building, an apartment, a hotel, or the like.
  • the refrigerating and air-conditioning apparatus 100c uses refrigeration cycles, in which refrigerants are circulated, so as to permit the cooling load and the cold-storage/refrigeration load to be simultaneously supplied.
  • points that are different from Embodiments 1 to 3 are mainly described, and the same components as those of Embodiments 1 to 3 are denoted by the same reference signs and description thereof is omitted.
  • the refrigerating and air-conditioning apparatus 100c has at least an air-conditioning refrigeration cycle 1c and a cold-storage/refrigeration refrigeration cycle 2c.
  • the air-conditioning refrigeration cycle 1c and the cold-storage/refrigeration refrigeration cycle 2c are formed such that, in a refrigerant-refrigerant heat exchanger 131c, heat is exchanged between a refrigerant of the air-conditioning refrigeration cycle 1c and a refrigerant of the cold-storage/refrigeration refrigeration cycle 2c while both the refrigerants are not mixed with each other.
  • the refrigerant circulated in the air-conditioning refrigeration cycle 1 c is referred to as a primary-side refrigerant, and the refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2c is referred to as a secondary-side refrigerant.
  • the air-conditioning refrigeration cycle 1 is formed of a heat source unit Ac, indoor units Bc (referred to as cooling indoor units Bc hereafter) that covers, for example, a cooling load, and a cold-storage/refrigeration booster unit Dc (in particular, a primary side of the refrigerant-refrigerant heat exchanger 131c) that serves as a heat source for the cold-storage/refrigeration refrigeration cycle 2c.
  • a heat source unit Ac indoor units Bc (referred to as cooling indoor units Bc hereafter) that covers, for example, a cooling load
  • a cold-storage/refrigeration booster unit Dc in particular, a primary side of the refrigerant-refrigerant heat exchanger 131c) that serves as a heat source for the cold-storage/refrigeration refrigeration cycle 2c.
  • the cooling indoor units Bc and the air-conditioning refrigeration cycle 1 side of the cold-storage/refrigeration booster unit Dc are connected in parallel to the heat source unit Ac.
  • the air-conditioning refrigeration cycle 1c side of the cold-storage/refrigeration booster unit Dc is referred to as a primary side of the cold-storage/refrigeration booster unit Dc
  • the cold-storage/refrigeration refrigeration cycle 2c side of the cold-storage/refrigeration booster unit Dc is referred to as a secondary side of the cold-storage/refrigeration booster unit Dc.
  • the heat source unit Ac supplies cooling energy to the cooling indoor units B and the primary side of the cold-storage/refrigeration booster unit Dc.
  • An air-conditioning compressor 101c, an outdoor heat exchanger (a heat-source side heat exchanger) 103c, and an accumulator 104c are connected in series by pipes and disposed in the heat source unit Ac.
  • a fan or another air-sending device which supplies air to the outdoor heat exchanger 103, be provided at a position close to the outdoor heat exchanger 103.
  • the air-conditioning compressor 101c suctions and compresses the primary-side refrigerant so as to cause the primary-side refrigerant to enter a high-temperature high-pressure state.
  • the outdoor heat exchanger 103c functions as a radiator (condenser) and causes heat to be exchanged between air supplied from the air-sending device (not shown) and the primary-side refrigerant, thereby condensing and liquefying the primary-side refrigerant.
  • the accumulator 104c is disposed on a suction side of the air-conditioning compressor 101c and stores the excessive primary-side refrigerant.
  • the accumulator 104c may be any container capable of storing the excessive primary-side refrigerant.
  • the cooling indoor units Bc receive cooling energy or heating energy supplied from the heat source unit Ac and cover the cooling load.
  • An air-conditioning expansion means 117c and an indoor heat exchanger (use-side heat exchangers) 118c are connected in series and disposed in each cooling indoor unit Bc. In the example illustrated in Fig. 5 , two cooling indoor units B are connected. In the cooling indoor units Bc, it is desirable that fans or other air-sending devices, which supply air to the indoor heat exchangers 118c, be provided at positions close to the indoor heat exchangers 118c.
  • the air-conditioning expansion means 117c which have functions of pressure reducing valves and expansion valves, reduce the pressure of the primary-side refrigerant and expand the primary-side refrigerant. It is desirable that the air-conditioning expansion means 117c include means such as means that can variably control opening degrees, for example, precision flow rate control means using electronic expansion valves, or inexpensive refrigerant flow rate regulating means such as capillary tubes.
  • the indoor heat exchangers 118c function as evaporators and cause heat to be exchanged between air supplied from the air-sending devices (not shown) and the primary-side refrigerant, thereby evaporating and gasifying the primary-side refrigerant.
  • the cold-storage/refrigeration booster unit Dc transfers cooling energy from the heat source unit Ac to the cold-storage/refrigeration refrigeration cycle 2c through the refrigerant-refrigerant heat exchanger 131c.
  • An expansion means 119c and the refrigerant-refrigerant heat exchanger 131c are connected in series on the primary side of the cold-storage/refrigeration booster unit Dc.
  • the air-conditioning refrigeration cycle 1c and the cold-storage/refrigeration refrigeration cycle 2c are connected to each other in a cascade manner with the refrigerant-refrigerant heat exchanger 131c. That is, the refrigerant-refrigerant heat exchanger 131c causes heat to be exchanged between the primary-side refrigerant and the secondary-side refrigerant.
  • the expansion means 119c which has the functions of a pressure reducing valve and an expansion valve, reduces the pressure of the primary-side refrigerant and expands the primary-side refrigerant. It is desirable that the expansion means 119c include a means such as a means that can variably control an opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the refrigerant-refrigerant heat exchanger 131c which functions as an evaporator, causes heat to be exchanged between the secondary-side refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2c and the primary-side refrigerant circulated in the air-conditioning refrigeration cycle 1c.
  • the air-conditioning refrigeration cycle 1c is established by the air-conditioning compressor 101c, the outdoor heat exchanger 103c, the air-conditioning expansion means 117c, the indoor heat exchangers 118c, and the accumulator 104c that are connected in series; the air-conditioning compressor 101c, the outdoor heat exchanger 103c, the expansion means 119c, the refrigerant-refrigerant heat exchanger 131c, and the accumulator 104c that are connected in series; and by the refrigerant circulating through these components.
  • the air-conditioning compressor 101c may be any that is capable of compressing the suctioned refrigerant into a high-pressure state, and is not limited to a specific type of compressor.
  • the air-conditioning compressor 101c may use one of a variety of compressors such as reciprocating, rotary, scroll, and screw compressors.
  • the rotation speed of the air-conditioning compressor 101c may be variably controllable by an inverter or may be fixed.
  • the type of the refrigerant circulated in the air-conditioning refrigeration cycle 1c is not particularly limited.
  • the refrigerant may be, for example, any one of a natural refrigerant such as carbon dioxide (CO2), hydrocarbon, or helium, an alternative refrigerant without chlorine such as HFC410A, HFC407C, or HFC404A, and a fluorocarbon refrigerant used in existing products such as R22 or R134a.
  • the primary-side refrigerant in a gaseous state is discharged from the air-conditioning compressor 101c and flows into the outdoor heat exchanger 103c.
  • the primary-side refrigerant in a superheated gas state having flowed into the outdoor heat exchanger 103c is cooled by air supplied to the outdoor heat exchanger 103c and liquefied.
  • This primary-side refrigerant flows out of the outdoor heat exchanger 103c, flows through a high-pressure side connection pipe 106c, and is distributed to the cooling indoor units Bc and the primary side of the cold-storage/refrigeration booster unit Dc.
  • the primary-side refrigerant having flowed into the cooling indoor units Bc is expanded by the air-conditioning expansion means 117c so as to have a low temperature and a low pressure, evaporates in the indoor heat exchangers 118c, and flows into a low-pressure side connection pipe 107c.
  • the primary-side refrigerant having flowed into the primary side of the cold-storage/refrigeration booster unit Dc is expanded by the expansion means 119c so as to have a low temperature and a low pressure, evaporates in the refrigerant-refrigerant heat exchanger 131c, and flows into the low-pressure side connection pipe 107c.
  • the primary-side refrigerant flowing in the low-pressure side connection pipe 107c then flows into the heat source unit A and returns to the air-conditioning compressor 101c through the accumulator 104c.
  • the cold-storage/refrigeration refrigeration cycle 2c is formed of the cold-storage/refrigeration booster unit Dc (in particular, the secondary side of the refrigerant-refrigerant heat exchanger 131) and a cold-storage/refrigeration unit Fc. That is, the cold-storage/refrigeration refrigeration cycle 2c includes a refrigeration compressor 130c disposed in the cold-storage/refrigeration booster unit Dc, the refrigerant-refrigerant heat exchanger 131c, refrigeration expansion means 132c, and a refrigeration heat exchanger 133c disposed in the cold-storage/refrigeration unit Fc that are connected in series by pipes.
  • the cold-storage/refrigeration refrigeration cycle 2c is connected to the air-conditioning refrigeration cycle 1c through the refrigerant-refrigerant heat exchanger 131c disposed in the cold-storage/refrigeration booster unit Dc.
  • the cold-storage/refrigeration booster unit Dc transfers cooling energy from the heat source unit Ac to the cold-storage/refrigeration refrigeration cycle 2c through the refrigerant-refrigerant heat exchanger 131c.
  • the refrigeration compressor 130c, the secondary side of the refrigerant-refrigerant heat exchanger 131c, and the refrigeration expansion means 132c are connected in series on the secondary side of the cold-storage/refrigeration booster unit Dc.
  • the refrigeration compressor 130c suctions and compresses the secondary-side refrigerant so as to cause the secondary-side refrigerant to enter a high-temperature high-pressure state.
  • the rotation speed of the refrigeration compressor 130c may be variably controllable by an inverter or may be fixed.
  • the refrigeration compressor 130c may be any that is capable of compressing the suctioned secondary-side refrigerant into a high-pressure state, and is not limited to a specific type of compressor.
  • the refrigeration compressor 130c may use one of a variety of compressors such as reciprocating, rotary, scroll, and screw compressors.
  • the refrigerant-refrigerant heat exchanger 131c causes heat to be exchanged between the primary-side refrigerant circulated in the air-conditioning refrigeration cycle 1c and the secondary-side refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2c.
  • the refrigeration expansion means 132c which has the functions of a pressure reducing valve and an expansion valve, reduces the pressure of the secondary-side refrigerant and expand the secondary-side refrigerant. It is desirable that the refrigeration expansion means 132c include a means such as a means that can variably control an opening degree, for example, a precision flow rate control means using an electronic expansion valve, or an inexpensive refrigerant flow rate regulating means such as a capillary tube.
  • the type of the secondary-side refrigerant circulated in the cold-storage/refrigeration refrigeration cycle 2c is not particularly limited.
  • the secondary-side refrigerant may be, for example, any one of a natural refrigerant such as carbon dioxide, hydrocarbon, or helium, an alternative refrigerant without chlorine such as HFC410A, HFC407C, or HFC404A, and a fluorocarbon refrigerant used in existing products such as R22 or R134a.
  • the cold-storage/refrigeration unit Fc receives cooling energy supplied from the cold-storage/refrigeration booster unit Dc and covers the cold-storage/refrigeration load.
  • the refrigeration heat exchanger 133c is disposed in the cold-storage/refrigeration unit Fc.
  • the refrigeration heat exchanger 133c is provided between the refrigeration expansion means 132c of the cold-storage/refrigeration booster unit Dc and the refrigeration compressor 130c, functions as an evaporator, causes heat to be exchanged between air supplied from the air-sending device (not shown) and the secondary-side refrigerant, and evaporates and gasifies the secondary-side refrigerant.
  • a fan or another air-sending device which supplies air to the refrigeration heat exchanger 133c, be provided at a position close to the refrigeration heat exchanger 133c.
  • the flows of the secondary-side refrigerant of the cold-storage/refrigeration booster unit Dc and the cold-storage/refrigeration unit Fc that is, the flow of the secondary-side refrigerant in the cold-storage/refrigeration refrigeration cycle 2c is similar to that of the secondary-side refrigerant in the cold-storage/refrigeration booster unit D and the cold-storage/refrigeration unit F described in Embodiments 1 to 3, that is, the flow of the secondary-side refrigerant in the cold-storage/refrigeration refrigeration cycle 2.
  • the refrigerating and air-conditioning apparatus 100c having such a configuration is intended for use, for example, in southern areas where weather is comparatively warm throughout the year, and is advantageous in cases where there are cooling loads and no heating load throughout the year.
  • an optimum load-side unit can be selected in accordance with the air-conditioning load (cooling load) and the cold-storage/refrigeration load.
  • the heat sources of the air-conditioning load and the cold-storage/refrigeration load are housed in a single unit (heat source unit A), the installation space can be decreased.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)

Claims (1)

  1. Appareil de réfrigération et de climatisation (100b) comprenant :
    un cycle de réfrigération par climatisation (1) formé en reliant en série un compresseur de climatisation (101), un échangeur thermique côté source de chaleur (103), un premier moyen d'expansion (117), et un échangeur thermique côté utilisation (118), et en reliant en série le compresseur de climatisation (101), l'échangeur thermique côté source de chaleur (103), un second moyen d'expansion (119), et un côté primaire d'un premier échangeur thermique réfrigérant/réfrigérant (131), le cycle de réfrigération par climatisation (1) provoquant la circulation d'un réfrigérant côté primaire à l'intérieur,
    le compresseur de climatisation (101) et l'échangeur thermique côté source de chaleur (103, 103c) étant contenus dans une unité de source de chaleur (A),
    le premier moyen d'expansion (117, 117c) et l'échangeur thermique côté utilisation (118, 118c) étant contenus dans une unité d'intérieur (B, C) ;
    au moins une unité de relais (E) reliée à un tuyau de raccordement côté haute pression (106) qui assure l'écoulement depuis l'unité de source de chaleur (A), et un tuyau de raccordement côté basse pression (107) qui assure l'écoulement vers l'unité de source de chaleur (A), respectivement ;
    l'appareil de réfrigération et de climatisation (100b) comprenant en outre : un cycle de réfrigération d'alimentation en eau chaude (3) formé en reliant en série un compresseur d'alimentation en eau chaude (140), un côté réfrigérant d'alimentation en eau chaude d'un échangeur thermique chaleur/réfrigérant (143), un quatrième moyen d'expansion (142), et un côté réfrigérant d'alimentation en eau chaude d'un second échangeur thermique réfrigérant/réfrigérant (141), le cycle de réfrigération d'alimentation en eau chaude (3) provoquant la circulation d'un réfrigérant d'alimentation en eau chaude à l'intérieur, le compresseur d'alimentation en eau chaude (140), le côté réfrigérant d'alimentation en eau chaude de l'échangeur thermique chaleur/réfrigérant (143), le quatrième moyen d'expansion (142), et le côté réfrigérant d'alimentation en eau chaude du second échangeur thermique réfrigérant/réfrigérant (141) étant contenus dans une unité de suralimentation de réfrigération dans laquelle l'énergie de chauffage stockée dans le réfrigérant côté primaire est transférée vers le réfrigérant d'alimentation en eau chaude par le biais du second échangeur thermique réfrigérant/réfrigérant (141) de façon pouvoir être utilisée comme une charge d'eau chaude, caractérisé par un cycle de réfrigération par stockage de froid/réfrigération (2) formé en reliant en série un compresseur de réfrigération (130), un côté secondaire du premier échangeur thermique réfrigérant/réfrigérant (131), un troisième moyen d'expansion (132), et un échangeur thermique de réfrigération (133), le cycle de réfrigération par stockage de froid/réfrigération (2) provoquant la circulation d'un réfrigérant côté secondaire à l'intérieur,
    le second moyen d'expansion (119), le premier échangeur thermique réfrigérant/réfrigérant (131), le compresseur de réfrigération (130) et le troisième moyen d'expansion (132) étant contenus dans une unité de suralimentation de réfrigération par stockage de froid/réfrigération (D) ; et
    la au moins une unité de relais (E) étant placée entre le cycle de réfrigération par climatisation (1) et le cycle de réfrigération par stockage de froid/réfrigération (2),
    dans lequel l'énergie de chauffage ou l'énergie de refroidissement stockée dans le réfrigérant côté primaire peut être utilisée comme charge de climatisation par le biais de l'échangeur thermique côté utilisation (118), et l'énergie de refroidissement stockée dans le réfrigérant côté primaire est transférée vers le réfrigérant côté secondaire par le biais du premier échangeur thermique réfrigérant/réfrigérant (131) de façon à pouvoir être utilisée comme charge de réfrigération par stockage de froid/réfrigération,
    et dans lequel l'unité de relais (E) est placée entre le cycle de réfrigération par climatisation (1) et le cycle de réfrigération par stockage de froid/réfrigération (2) et le cycle de réfrigération d'alimentation en eau chaude (3).
EP10853187.2A 2010-06-18 2010-06-18 Dispositif de climatisation à réfrigération Not-in-force EP2584285B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/004088 WO2011158305A1 (fr) 2010-06-18 2010-06-18 Dispositif de climatisation à réfrigération

Publications (3)

Publication Number Publication Date
EP2584285A1 EP2584285A1 (fr) 2013-04-24
EP2584285A4 EP2584285A4 (fr) 2014-03-19
EP2584285B1 true EP2584285B1 (fr) 2018-02-21

Family

ID=45347733

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10853187.2A Not-in-force EP2584285B1 (fr) 2010-06-18 2010-06-18 Dispositif de climatisation à réfrigération

Country Status (5)

Country Link
US (1) US20130061622A1 (fr)
EP (1) EP2584285B1 (fr)
JP (1) JPWO2011158305A1 (fr)
CN (1) CN102947653A (fr)
WO (1) WO2011158305A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8011191B2 (en) 2009-09-30 2011-09-06 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
EP2927614B1 (fr) * 2012-11-29 2020-08-05 Mitsubishi Electric Corporation Dispositif de climatisation
EP2975335B1 (fr) * 2013-03-12 2018-12-05 Mitsubishi Electric Corporation Climatiseur
DE102014203895B4 (de) * 2014-03-04 2018-08-16 Konvekta Ag Kälteanlage
KR102264725B1 (ko) * 2014-05-22 2021-06-11 엘지전자 주식회사 히트 펌프
WO2016189810A1 (fr) * 2015-05-28 2016-12-01 パナソニックＩｐマネジメント株式会社 Dispositif de pompe à chaleur
CN109386989B (zh) * 2018-10-22 2020-07-28 广东美的暖通设备有限公司 两管制喷气增焓室外机及多联机系统

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5241829A (en) * 1989-11-02 1993-09-07 Osaka Prefecture Government Method of operating heat pump
MY114473A (en) * 1997-04-08 2002-10-31 Daikin Ind Ltd Refrigerating system
JP4221780B2 (ja) * 1998-07-24 2009-02-12 ダイキン工業株式会社 冷凍装置
JP2002277098A (ja) * 2001-03-21 2002-09-25 Daikin Ind Ltd 冷凍装置
US7188490B2 (en) * 2003-01-17 2007-03-13 Samsung Electronics Co., Ltd. Refrigerator
JP4488767B2 (ja) 2004-03-02 2010-06-23 三洋電機株式会社 空調冷凍装置
JP4599910B2 (ja) * 2004-07-01 2010-12-15 ダイキン工業株式会社 給湯装置
JP4660334B2 (ja) 2005-09-30 2011-03-30 三洋電機株式会社 冷凍システム
JP2007139274A (ja) * 2005-11-16 2007-06-07 Hitachi Ltd 空気調和機
JP5197576B2 (ja) * 2007-03-27 2013-05-15 三菱電機株式会社 ヒートポンプ装置
US20110016897A1 (en) * 2008-02-04 2011-01-27 Mitsubishi Electric Corporation Air conditioning-hot water supply combined system
WO2009122477A1 (fr) * 2008-03-31 2009-10-08 三菱電機株式会社 Système complexe de climatisation et de fourniture d'eau chaude
KR101151529B1 (ko) * 2009-11-20 2012-05-30 엘지전자 주식회사 냉매시스템
KR101639814B1 (ko) * 2009-11-20 2016-07-22 엘지전자 주식회사 냉장 및 냉동 복합 공조시스템
KR101155496B1 (ko) * 2010-04-23 2012-06-15 엘지전자 주식회사 히트펌프식 급탕장치

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
EP2584285A4 (fr) 2014-03-19
WO2011158305A1 (fr) 2011-12-22
US20130061622A1 (en) 2013-03-14
EP2584285A1 (fr) 2013-04-24
CN102947653A (zh) 2013-02-27
JPWO2011158305A1 (ja) 2013-08-15

Similar Documents

Publication Publication Date Title
US9593872B2 (en) Heat pump
US9683768B2 (en) Air-conditioning apparatus
US9032747B2 (en) Multi-mode air conditioner with refrigerant cycle and heat medium cycle
EP2615392B1 (fr) Pompe de chaleur en cascade
US9829210B2 (en) Air-conditioning apparatus and method for controlling air-conditioning apparatus by ranking capacities for use-side heat exchangers
US9903601B2 (en) Air-conditioning apparatus
EP2492614B1 (fr) Dispositif de conditionnement d'air
US9441851B2 (en) Air-conditioning apparatus
US9353958B2 (en) Air-conditioning apparatus
US8943849B2 (en) Air-conditioning apparatus
EP2503266B1 (fr) Dispositif à cycle de réfrigération et procédé de propagation d'informations adapté à celui-ci
EP2527751B1 (fr) Système combiné de climatisation et d'alimentation en eau chaude
EP2960602B1 (fr) Climatiseur
US9435549B2 (en) Air-conditioning apparatus with relay unit
EP2584285B1 (fr) Dispositif de climatisation à réfrigération
US9140459B2 (en) Heat pump device
EP2541169A1 (fr) Dispositif de conditionnement d'air, et système d'alimentation en eau chaude pour conditionneur d'air
US9285142B2 (en) Refrigeration cycle apparatus
US7533539B2 (en) Refrigerating machine
US20120204585A1 (en) Air-conditioning apparatus
EP3839365B1 (fr) Système de climatisation
US9335074B2 (en) Air-conditioning apparatus
CN108759150B (zh) 空调系统和其控制方法
WO2015177852A1 (fr) Dispositif à cycle de réfrigération

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20121205

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20140213

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 1/00 20060101ALI20140207BHEP

Ipc: F25B 29/00 20060101ALI20140207BHEP

Ipc: F25B 7/00 20060101AFI20140207BHEP

17Q First examination report despatched

Effective date: 20161108

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170907

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602010048735

Country of ref document: DE

Ref country code: AT

Ref legal event code: REF

Ref document number: 972196

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180221

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 972196

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180221

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180521

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180521

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602010048735

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20181122

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180630

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180618

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180618

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180618

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180221

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20100618

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180221

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180621

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20200824

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602010048735

Country of ref document: DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20210525

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20210526

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602010048735

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20220618

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220618

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230103