EP2503266B1 - Dispositif à cycle de réfrigération et procédé de propagation d'informations adapté à celui-ci - Google Patents

Dispositif à cycle de réfrigération et procédé de propagation d'informations adapté à celui-ci Download PDF

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Publication number
EP2503266B1
EP2503266B1 EP09851418.5A EP09851418A EP2503266B1 EP 2503266 B1 EP2503266 B1 EP 2503266B1 EP 09851418 A EP09851418 A EP 09851418A EP 2503266 B1 EP2503266 B1 EP 2503266B1
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EP
European Patent Office
Prior art keywords
hot
unit
refrigerant
water supply
refrigeration cycle
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
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EP09851418.5A
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German (de)
English (en)
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EP2503266A1 (fr
EP2503266A4 (fr
Inventor
Kenji Matsui
Shigeo Takata
Hironori Yabuuchi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2503266A1 publication Critical patent/EP2503266A1/fr
Publication of EP2503266A4 publication Critical patent/EP2503266A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters

Definitions

  • the present invention relates to a refrigeration cycle apparatus used in an air-conditioning apparatus or an air-conditioning hot-water supply combined system and an information transfer method used in the refrigeration cycle apparatus, and to a refrigeration cycle apparatus that increases system COP and an information transfer method used in the refrigeration cycle apparatus.
  • EP 1 275 913 A2 refers to a multiform gas heat pump type of air conditioning system having: a plurality of indoor units that are each provided with an indoor heat exchanger and that perform a heat exchange between air inside a room and refrigerant; an outdoor unit provided with a compressor driven by a gas engine and an outdoor heat exchanger for performing a heat exchange between outside air and the refrigerant; and a split flow control unit for controlling a flow direction of the refrigerant in each of the indoor units and for performing a selection switching between cooling and heating operations.
  • EP 1 340 949 A1 refers to a multi-stage type refrigeration system including a chiller unit and a freezer unit by eliminating a cascade unit.
  • the freezer unit is provided with a freezing compressor for compressing a refrigerant in a total of two stages together with compressors in an outdoor unit.
  • the freezing compressor is formed by an inverter compressor.
  • An oil separator is disposed on the discharge of the freezing compressor, a heat exchanger is provided for cooling an inverter with an refrigeration oil separated by the oil separator and a suction refrigerant.
  • US2006/0218948 also discloses a multi use-side unit cooling and/or heating system.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 11-270920 ( Fig. 1 etc.)
  • the present invention has been made in order to overcome the above problems, and an object thereof is to provide a refrigeration cycle apparatus that achieves load balancing (for example, the balance between a cooling load and the heating load and the balance between the cooling load and the heating and hot water loads) to increase system COP and an information transfer method used in the refrigeration cycle apparatus.
  • load balancing for example, the balance between a cooling load and the heating load and the balance between the cooling load and the heating and hot water loads
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus according to claim 1.
  • An information transfer method according to the present invention is an information transfer method used in the above refrigeration cycle apparatus, wherein the method is as according to claim 7.
  • a refrigeration cycle apparatus allows a plurality of use-side units to be operated so that the thermal cooling load and the thermal heating load to be executed by the plurality of use-side units are balanced, and can therefore increase system COP and achieve a reduction in running cost while realizing energy saving.
  • An information transfer method according to the present invention is used in the above refrigeration cycle apparatus. Therefore, a stable operation can be efficiently continued.
  • Fig. 1 is a refrigerant circuit diagram illustrating an example of the refrigerant circuit configuration of a refrigeration cycle apparatus 100 according to an embodiment of the present invention.
  • the refrigerant circuit configuration and operation of the refrigeration cycle apparatus 100 will be described with reference to Fig. 1 .
  • Fig. 1 a case where the refrigeration cycle apparatus 100 is an air-conditioning hot-water supply combined system capable of simultaneously supplying a cooling load (thermal cooling load) and heating and hot water loads (thermal heating load) by utilizing a refrigeration cycle in which a refrigerant (air conditioning refrigerant) is circulated is illustrated by way of example. It should be noted that the dimensional relationships of components in Fig. 1 and other subsequent figures may be different from the actual ones.
  • the refrigeration cycle apparatus 100 is constituted by a refrigeration cycle for air conditioning 1, a refrigeration cycle for hot-water supply 2, and a hot-water supply device 3, and is configured such that the refrigeration cycle for air conditioning 1 and the refrigeration cycle for hot-water supply 2 exchange heat in a refrigerant-to-refrigerant heat exchanger 41 and the refrigeration cycle for hot-water supply 2 and the hot-water supply device 3 exchange heat in a heat medium-to-refrigerant heat exchanger 51 without each of the refrigerants and water being mixed.
  • the refrigeration cycle apparatus 100 further has mounted therein a hot-water supply unit F.
  • the refrigeration cycle for air conditioning 1 is constituted by a heat source unit A, an indoor unit B and an indoor unit C each of which takes charge of the cooling load or the heating load, a heat source circuit for hot-water supply D serving as a heat source of the refrigeration cycle for hot-water supply 2, and a relay unit E.
  • the indoor unit B, the indoor unit C, and the heat source circuit for hot-water supply D are connected in parallel to the heat source unit A and mounted.
  • the relay unit E which is disposed between the heat source unit A and the other components, that is, the indoor unit B, the indoor unit C, and the heat source circuit for hot-water supply D, switches a flow of a refrigerant to cause the indoor unit B, the indoor unit C, and the heat source circuit for hot-water supply D to perform their respective functions.
  • the heat source unit A has a function for supplying heating energy or cooling energy to the indoor unit B, the indoor unit C, and the heat source circuit for hot-water supply D.
  • the heat source unit A has mounted therein an air conditioning compressor 101, a four-way valve 102, an outdoor heat exchanger (heat source side heat exchanger) 103, and an accumulator 104, which are connected in series.
  • the air conditioning compressor 101 is configured to suck in the air conditioning refrigerant and compress the air conditioning refrigerant into a high-temperature high-pressure state.
  • the four-way valve 102 is configured to switch the flow of the air conditioning refrigerant.
  • the outdoor heat exchanger 103 functions as an evaporator or a radiator (condenser), and is configured to exchange heat between air supplied from a fan or the like (not illustrated) and the air conditioning refrigerant to evaporate and gasify the air conditioning refrigerant or condense and liquefy the air conditioning refrigerant.
  • the accumulator 104 is disposed on the suction side of the air conditioning compressor 101, and is configured to store excessive air conditioning refrigerant.
  • the accumulator 104 may be any container capable of storing excessive air conditioning refrigerant.
  • a check valve 105a is provided in a high-pressure-side connection pipe 106 between the outdoor heat exchanger 103 and the relay unit E for permitting the air conditioning refrigerant to flow only in a predetermined direction (the direction from the heat source unit A to the relay unit E), and a check valve 105b is provided in a low-pressure-side connection pipe 107 between the four-way valve 102 and the relay unit E for permitting the air conditioning refrigerant to flow only in a predetermined direction (the 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 through a first connection pipe 130 that connects the upstream side (connection portion a) of the check valve 105a and the upstream side (connection portion c) of the check valve 105b and through a second connection pipe 131 that connects the downstream side (connection portion b) of the check valve 105a and the downstream side (connection portion d) of the check valve 105b.
  • a check valve 105c is provided in the first connection pipe 130 for permitting the air conditioning refrigerant to be distributed only in the direction from the low-pressure-side connection pipe 107 to the high-pressure-side connection pipe 106.
  • a check valve 105d is provided in the second connection pipe 131 for permitting the air conditioning refrigerant to be distributed only in the direction from the low-pressure-side connection pipe 107 to the high-pressure-side connection pipe 106.
  • Each of the indoor unit B and the indoor unit C has a function of taking charge of the heating load or the cooling load upon receipt of heating energy or cooling energy supplied from the heat source unit A.
  • Each of the indoor unit B and the indoor unit C has mounted therein air conditioning expansion devices 117 and indoor heat exchangers (use side heat exchangers) 118, which are connected in series.
  • the indoor unit B and the indoor unit C, each of which has mounted therein two air conditioning expansion devices 117 and two indoor heat exchangers 118 in such a manner the two air conditioning expansion devices 117 are parallel to each other and the two indoor heat exchangers 118 are parallel to each other, are illustrated by way of example.
  • connection pipes 133 connection pipes that connect the relay unit E to the indoor heat exchangers 118
  • connection pipes 134 connection pipes that connect the relay unit E to the air conditioning expansion devices 117
  • the air conditioning expansion devices 117 function as pressure reducing valves and expansion valves, and are configured to reduce the pressure of the air conditioning refrigerant to cause the air conditioning refrigerant to expand.
  • Each of the air conditioning expansion devices 117 may be constituted by a mechanism whose opening degree is variably controllable, such as a precise flow rate control device based on an electronic expansion valve or an inexpensive refrigerant flow rate regulating device such as a capillary tube.
  • the indoor heat exchangers 118 function as radiators (condensers) or evaporators, and are configured to exchange heat between air supplied from the fan or the like (not illustrated) and the air conditioning refrigerant to evaporate and gasify the air conditioning refrigerant or condense and liquefy the air conditioning refrigerant.
  • the air conditioning expansion devices 117 and the indoor heat exchangers 118 are connected in series.
  • the heat source circuit for hot-water supply D has a function for supplying the heating energy or cooling energy from the heat source unit A to the refrigeration cycle for hot-water supply 2 via the refrigerant-to-refrigerant heat exchanger 41.
  • the heat source circuit for hot-water supply D is configured such that a heat source expansion device for hot-water supply 119 and the refrigerant-to-refrigerant heat exchanger 41 are connected in series. That is, the refrigeration cycle for air conditioning 1 and the refrigeration cycle for hot-water supply 2 are cascade-connected via the refrigerant-to-refrigerant heat exchanger 41.
  • connection pipe 135 a connection pipe that connects the relay unit E to the refrigerant-to-refrigerant heat exchanger 41
  • connection pipe 136 a connection pipe that connects the relay unit E to the heat source expansion device for hot-water supply 119.
  • the heat source expansion device for hot-water supply 119 functions as a pressure reducing valve and an expansion valve, and is configured to reduce the pressure of the air conditioning refrigerant to cause the air conditioning refrigerant to expand.
  • the heat source expansion device for hot-water supply 119 may be constituted by a mechanism whose opening degree is variably controllable, such as a precise flow rate control device based on an electronic expansion valve or an inexpensive refrigerant flow rate regulating device such as a capillary tube.
  • the refrigerant-to-refrigerant heat exchanger 41 functions as a radiator (condenser) or an evaporator, and is configured to exchange heat between the hot-water supply refrigerant circulating in the refrigeration cycle of the refrigeration cycle for hot-water supply 2 and the air conditioning refrigerant circulating in the refrigeration cycle of the refrigeration cycle for air conditioning 1.
  • the relay unit E connects the use-side units (the indoor unit B, the indoor unit C, and the heat source circuit for hot-water supply D) and the heat source unit A, and has a function of determining whether the indoor heat exchangers 118 are to be radiators or evaporators and the refrigerant-to-refrigerant heat exchanger 41 is to be a water cooler or a water heater by opening and closing either valve means 109a or valve means 109b of a first distribution unit 109.
  • the relay unit E is constituted by a gas-liquid separator 108, the first distribution unit 109, a second distribution unit 110, a first internal heat exchanger 111, a first relay expansion device 112, a second internal heat exchanger 113, and a second relay expansion device 114.
  • connection pipes 133 and the connection pipe 135 each branch into two pipes, first pipes (connection pipes 133b and a connection pipe 135b) of which are connected to the low-pressure-side connection pipe 107 and second pipes (connection pipes 133a and a connection pipe 135a) of which are connected to a connection pipe (referred to as a connection pipe 132) connected to the gas-liquid separator 108.
  • the valve means 109a that are controlled to be opened or closed to allow the refrigerant to pass or not pass therethrough are provided in the connection pipes 133a and the connection pipe 135a
  • the valve means 109b that are controlled to be opened or closed to allow the refrigerant to pass or not pass therethrough are provided in the connection pipes 133b and the connection pipe 135b.
  • connection pipes 134 and the connection pipe 136 each branch into two pipes, first pipes (connection pipes 134a and a connection pipe 136a) of which are connected to a first junction unit 115 and second pipes (connection pipes 134b and a connection pipe 136b) of which are connected to a second junction unit 116.
  • second distribution unit 110 furthermore, check valves 110a that permit the refrigerant to be distributed only in one direction are provided in the connection pipes 134a and the connection pipe 136a, and check valves 110b that permit the refrigerant to be distributed only in one direction are provided in the connection pipes 134b and the connection pipe 136b.
  • the first junction unit 115 is connected to the gas-iiquid separator 108 from the second distribution unit 110 via the first relay expansion device 112 and the first internal heat exchanger 111.
  • the second junction unit 116 branches into pipes between the second distribution unit 110 and the second internal heat exchanger 113, one pipe being connected via the second internal heat exchanger 113 to the first junction unit 115 between the second distribution unit 110 and the first relay expansion device 112 and the other pipe (a second junction unit 116a) being connected to the low-pressure-side connection pipe 107 via the second relay expansion device 114, the second internal heat exchanger 113, and the first internal heat exchanger 111.
  • the gas-liquid separator 108 is configured to separate the air conditioning refrigerant into gas refrigerant and liquid refrigerant, and is provided in the high-pressure-side connection pipe 106.
  • the gas-liquid separator 108 has one end connected to the valve means 109a of the first distribution unit 109 and another end connected to the second distribution unit 110 through the first junction unit 115.
  • the first distribution unit 109 has a function of allowing the air conditioning refrigerant to flow into the indoor heat exchangers 118 and the refrigerant-to-refrigerant heat exchanger 41 by either the valve means 109a or the valve means 109b being opened or closed.
  • the second distribution unit 110 has a function of permitting the air conditioning refrigerant to flow in either one direction through each of the check valves 110a and check valves 110b.
  • the first internal heat exchanger 111 is provided in the first junction unit 115 between the gas-liquid separator 108 and the first relay expansion device 112, and is configured to exchange heat between the air conditioning refrigerant passing through the first junction unit 115 and the air conditioning refrigerant passing through the second junction unit 116a branching from the second junction unit 116.
  • the first relay expansion device 112 is provided in the first junction unit 115 between the first internal heat exchanger 111 and the second distribution unit 110, and is configured to reduce the pressure of the air conditioning refrigerant to cause the air conditioning refrigerant to expand.
  • the first relay expansion device 112 may be constituted by a mechanism whose opening degree is variably controllable, such as a precise flow rate control device based on an electronic expansion valve or an inexpensive refrigerant flow rate regulating device such as a capillary tube.
  • the second internal heat exchanger 113 is provided in the second junction unit 116, and is configured to exchange heat between the air conditioning refrigerant passing through the second junction unit 116 and the air conditioning refrigerant passing through the second junction unit 116a branching from the second junction unit 116.
  • the second relay expansion device 114 is provided in the second junction unit 116 between the second internal heat exchanger 113 and the second distribution unit 110.
  • the second relay expansion device 114 functions as a pressure reducing valve and an expansion valve, and is configured to reduce the pressure of the air conditioning refrigerant to cause the air conditioning refrigerant to expand.
  • the second relay expansion device 114 may be constituted by a mechanism whose opening degree is variably controllable, such as a precise flow rate control device based on an electronic expansion valve or an inexpensive refrigerant flow rate regulating device such as a capillary tube.
  • the refrigeration cycle for air conditioning 1 constitutes a first refrigerant circuit in which the air conditioning compressor 101, the four-way valve 102, the indoor heat exchangers 118, the air conditioning expansion devices 117, and the outdoor heat exchanger 103 are connected in series, in which the air conditioning compressor 101, the four-way valve 102, the refrigerant-to-refrigerant heat exchanger 41, the heat source expansion device for hot-water supply 119, and the outdoor heat exchanger 103 are connected in series, and in which the indoor heat exchangers 118 and the refrigerant-to-refrigerant heat exchanger 41 are connected in parallel via the relay unit E, and is established by circulating an air conditioning refrigerant in the first refrigerant circuit.
  • the air conditioning compressor 101 may be of any type capable of compressing a sucked refrigerant into a high-pressure state, and the type thereof is not particularly limited.
  • the air conditioning compressor 101 may be of any of various types such as reciprocating, rotary, scroll, and screw types.
  • the air conditioning compressor 101 may also be of a type whose rotation speed is variably controllable by an inverter, or of a type whose rotation speed is fixed.
  • the kind of refrigerant circulating in the refrigeration cycle for air conditioning 1 is not particularly limited, and natural refrigerants such as carbon dioxide (CO 2 ), hydrocarbon, and helium, alternative chlorine-free refrigerants such as HFC410A, HFC407C, and HFC404A, and fluorocarbon refrigerants used in existing products, such as R22 and R134a, may be used.
  • natural refrigerants such as carbon dioxide (CO 2 ), hydrocarbon, and helium
  • alternative chlorine-free refrigerants such as HFC410A, HFC407C, and HFC404A
  • fluorocarbon refrigerants used in existing products such as R22 and R134a
  • the air conditioning refrigerant compressed into a high-temperature high-pressure refrigerant by the air conditioning compressor 101 is discharged from the air conditioning compressor 101, traveling through the four-way valve 102, passing through the check valve 105c, introduced into the high-pressure-side connection pipe 106, and flows into the gas-liquid separator 108 of the relay unit E in a superheated gaseous state.
  • the air conditioning refrigerant in the superheated gaseous state flowing into the gas-liquid separator 108 is distributed to circuits of the first distribution unit 109 in which the valve means 109a are open.
  • the air conditioning refrigerant in the superheated gaseous state flows into the indoor unit C and the heat source circuit for hot-water supply D.
  • the air conditioning refrigerants flowing into the indoor unit C transfer heat in the indoor heat exchangers 118 (to thereby warm indoor air), undergo pressure reduction in the air conditioning expansion devices 117, and merge in the first junction unit 115. Also, the air conditioning refrigerant flowing into the heat source circuit for hot-water supply D transfers heat in the refrigerant-to-refrigerant heat exchanger 41 (to thereby supply heat to the refrigeration cycle for hot-water supply 2), undergoes pressure reduction in the heat source expansion device for hot-water supply 119, and merges with the air conditioning refrigerants flowing from the indoor unit C in the first junction unit 115.
  • the portion of the air conditioning refrigerant in the superheated gaseous state output from the first internal heat exchanger 111 travels through the first relay expansion device 112, and merges with the air conditioning refrigerant that has been used for air conditioning (air conditioning refrigerants that have flowed into the indoor unit C and the heat source circuit for hot-water supply D and that have transferred heat in the indoor heat exchangers 118 and the refrigerant-to-refrigerant heat exchanger 41) in the first junction unit 115.
  • the portion of the air conditioning refrigerant in the superheated gaseous state to travel through the first relay expansion device 112 may be prevented from traveling through the first relay expansion device 112 by fully closing the first relay expansion device 112. After that, the portion of the air conditioning refrigerant in the superheated gaseous state exchanges heat, in the second internal heat exchanger 113, with the air conditioning refrigerant that has been expanded and has become a low-temperature low-pressure refrigerant in the second relay expansion device 114 to obtain a degree of supercooling.
  • This air conditioning refrigerant is distributed to the second junction unit 116 side and to the second relay expansion device 114 side.
  • the air conditioning refrigerant passing through the second junction unit 116 is distributed to circuits in which the valve means 109b are open.
  • the air conditioning refrigerant passing through the second junction unit 116 flows into the indoor unit B, and is caused to expand into low-temperature low-pressure refrigerants by the air conditioning expansion devices 117.
  • the low-temperature low-pressure refrigerants evaporate in the indoor heat exchangers 118, traveling through the valve means 109b, and merge in the low-pressure-side connection pipe 107.
  • the air conditioning refrigerant passing through the second relay expansion device 114 evaporates by heat exchange in the second internal heat exchanger 113 and the first internal heat exchanger 111, and merges with the air conditioning refrigerants flowing from the indoor unit B in the low-pressure-side connection pipe 107.
  • the merged air conditioning refrigerant in the low-pressure-side connection pipe 107 is introduced into the outdoor heat exchanger 103 through the check valve 105d, where liquid refrigerant that may remain depending on operating conditions is evaporated, and returns to the air conditioning compressor 101 through the four-way valve 102 and the accumulator 104.
  • the refrigeration cycle for hot-water supply 2 is constituted by a hot-water supply compressor 21, the heat medium-to-refrigerant heat exchanger 51, a hot-water supply expansion device 22, and the refrigerant-to-refrigerant heat exchanger 41. That is, the refrigeration cycle for hot-water supply 2 constitutes a second refrigerant circuit in which the hot-water supply compressor 21, the heat medium-to-refrigerant heat exchanger 51, the hot-water supply expansion device 22, and the refrigerant-to-refrigerant heat exchanger 41 are connected in series by a refrigerant pipe 45, and is established by circulating the hot-water supply refrigerant in the second refrigerant circuit.
  • the hot-water supply compressor 21 is configured to suck in the hot-water supply refrigerant and compress the hot-water supply refrigerant into a high-temperature high-pressure state.
  • the hot-water supply compressor 21 may be of a type whose rotation speed is variably controllable by an inverter, or of a type whose rotation speed is fixed. Furthermore, the hot-water supply compressor 21 may be of any type capable of compressing a sucked refrigerant into a high-pressure state, and the type thereof is not particularly limited.
  • the hot-water supply compressor 21 may be constituted by any of various types such as reciprocating, rotary, scroll, and screw types.
  • the heat medium-to-refrigerant heat exchanger 51 is configured to exchange heat between the heat medium (fluid such as water) circulating in the hot-water supply device 3 and the hot-water supply refrigerant circulating in the refrigeration cycle for hot-water supply 2. That is, the refrigeration cycle for hot-water supply 2 and the hot-water supply device 3 are cascade-connected via the heat medium-to-refrigerant heat exchanger 51.
  • the hot-water supply expansion device 22 functions as a pressure reducing valve and an expansion valve, and is configured to reduce the pressure of the hot-water supply refrigerant to cause the hot-water supply refrigerant to expand.
  • the hot-water supply expansion device 22 may be constituted by a mechanism whose opening degree is variably controllable, such as a precise flow rate control device based on an electronic expansion valve or an inexpensive refrigerant flow rate regulating device such as a capillary tube.
  • the refrigerant-to-refrigerant heat exchanger 41 is configured to exchange heat between the hot-water supply refrigerant circulating in the refrigeration cycle for hot-water supply 2 and the air conditioning refrigerant circulating in the refrigeration cycle for air conditioning 1.
  • the kind of refrigerant circulating in the refrigeration cycle for hot-water supply 2 is not particularly limited, and natural refrigerants such as carbon dioxide, hydrocarbon, and helium, alternative chlorine-free refrigerants such as HFC410A, HFC407C, and HFC404A, and fluorocarbon refrigerants used in existing products, such as R22 and R134a, may be used.
  • the hot-water supply refrigerant compressed into a high-temperature high-pressure refrigerant by the hot-water supply compressor 21 is discharged from the hot-water supply compressor 21, and flows into the heat medium-to-refrigerant heat exchanger 51.
  • the flowing hot-water supply refrigerant transfers heat by heating the water circulating in the hot-water supply device 3.
  • the hot-water supply refrigerant is expanded by the hot-water supply expansion device 22 until its temperature has dropped to less than or equal to the outlet temperature of the refrigerant-to-refrigerant heat exchanger 41 in the heat source circuit for hot-water supply D of the refrigeration cycle for air conditioning 1.
  • the expanded hot-water supply refrigerant receives heat from the air conditioning refrigerant flowing in the heat source circuit for hot-water supply D included in the refrigeration cycle for air conditioning 1, evaporates in the refrigerant-to-refrigerant heat exchanger 41, and returns to the hot-water supply compressor 21.
  • the hot-water supply device 3 is constituted by a water circulation pump 31, the heat medium-to-refrigerant heat exchanger 51, and a hot-water storage tank 32. That is, the hot-water supply device 3 constitutes a water circuit (heat medium circuit) in which the water circulation pump 31, the heat medium-to-refrigerant heat exchanger 51, and the hot-water storage tank 32 are connected in series by a stored hot-water/water circulating pipe 203, and is established by circulating water for hot-water supply in the water circuit.
  • the stored hot-water/water circulating pipe 203 included in the water circuit is composed of a copper tube, a stainless tube, a steel tube, a vinyl chloride pipe, or the like.
  • the water circulation pump 31 is configured to suck in the water stored in the hot-water storage tank 32, pressurize the water, and circulate the water in the hot-water supply device 3.
  • the water circulation pump 31 may be of a type whose rotation speed is controlled by an inverter, by way of example.
  • the heat medium-to-refrigerant heat exchanger 51 is configured to exchange heat between the heat medium (fluid such as water) circulating in the hot-water supply device 3 and the hot-water supply refrigerant circulating in the refrigeration cycle for hot-water supply 2.
  • the hot-water storage tank 32 is configured to store the water heated by the heat medium-to-refrigerant heat exchanger 51.
  • comparatively low temperature water stored in the hot-water storage tank 32 is drawn out of the bottom of the hot-water storage tank 32 and is pressurized by the water circulation pump 31.
  • the water pressurized by the water circulation pump 31 flows into the heat medium-to-refrigerant heat exchanger 51, and receives heat in the heat medium-to-refrigerant heat exchanger 51 from the hot-water supply refrigerant circulating in the refrigeration cycle for hot-water supply 2. That is, the water flowing into the heat medium-to-refrigerant heat exchanger 51 is boiled by the hot-water supply refrigerant circulating in the refrigeration cycle for hot-water supply 2, and its temperature rises. The boiled water returns to a comparatively high temperature upper portion of the hot-water storage tank 32, and is stored in the hot-water storage tank 32.
  • the refrigeration cycle for air conditioning 1 and the refrigeration cycle for hot-water supply 2 have independent refrigerant circuit configurations (the first refrigerant circuit constituting the refrigeration cycle for air conditioning 1 and the second refrigerant circuit constituting the refrigeration cycle for hot-water supply 2).
  • the refrigerants to be circulated in the respective refrigerant circuits may be of the same type or of different types. That is, the refrigerants in the respective refrigerant circuits flow so as to exchange heat in the refrigerant-to-refrigerant heat exchanger 41 and the heat medium-to-refrigerant heat exchanger 51 without being mixed.
  • a refrigerant with a low critical temperature When a refrigerant with a low critical temperature is used as a hot-water supply refrigerant, the hot-water supply refrigerant in the heat transferring process performed by the heat medium-to-refrigerant heat exchanger 51 is assumed to enter a supercritical state during high-temperature hot-water supply.
  • the COP largely fluctuates due to changes in the radiator pressure and the radiator outlet temperature. In order to operate with high COP, more sophisticated control is demanded.
  • a refrigerant with a low critical temperature has a higher saturation pressure than other refrigerants for the same temperature, and the thickness of the pipes and compressors needs to be increased accordingly, resulting in an increase in cost.
  • the target temperature of hot-water supply is assumed to be typically 60 degrees C or higher at minimum.
  • a refrigerant having a critical temperature of 60 degrees C or higher at minimum is used as the hot-water supply refrigerant.
  • high COP can be achieved more stably with lower cost. It is anticipated that temperature and pressure will become high in the refrigerant circuit when the refrigerant is commonly used around the critical temperature. Using a high pressure shell type compressor as the hot-water supply compressor 21 enables stable operation.
  • the invention is not limited to this, and the accumulator 104 may be omitted if excessive refrigerant is stored in a heat exchanger serving as a radiator in a refrigeration cycle.
  • the number of indoor units to be connected is not particularly limited, and, for example, one or more indoor units B and no indoor unit C or one or more indoor units C may be connected.
  • the capacities of indoor units included in the refrigeration cycle for air conditioning 1 may be the same or different from high to low.
  • the hot water load system uses a binary cycle.
  • a demand for high-temperature hot-water supply for example, 80 degrees C
  • it is only required to set the temperature of the radiator of the refrigeration cycle for hot-water supply 2 to a high temperature for example, a condensing temperature of 85 degrees C.
  • a high temperature for example, a condensing temperature of 85 degrees C.
  • the condensing temperature for example, 50 degrees C
  • energy saving is achieved.
  • a demand for high-temperature hot-water supply during the air conditioning cooling operation in the summer would conventionally need to be provided through a boiler or the like. Because hot-water supply is performed through collection and reuse of heating energy, which has been conventionally released in the air, the system COP is significantly increased, leading to energy saving.
  • the hot-water supply unit F has mounted therein the refrigerant-to-refrigerant heat exchanger 41, the heat source expansion device for hot-water supply 119, the heat medium-to-refrigerant heat exchanger 51, the hot-water supply compressor 21, and the hot-water supply expansion device 22. That is, the hot-water supply unit F accommodates therein a portion of the refrigeration cycle for air conditioning 1 via the refrigerant-to-refrigerant heat exchanger 41, the entirety of the refrigeration cycle for hot-water supply 2, and a portion of the hot-water supply device 3 via the heat medium-to-refrigerant heat exchanger 51.
  • Fig. 2 is a schematic configuration diagram for explaining information transfer in the refrigeration cycle apparatus 100 according to an embodiment of the present invention. The information transfer performed by the refrigeration cycle apparatus 100 will be described with reference to Figs. 1 and 2 .
  • the refrigeration cycle apparatus 100 in which two indoor units (an indoor unit B and an indoor unit C) and two hot-water supply units F (a hot-water supply unit F1 and a hot-water supply unit F2) are connected to one heat source unit A is illustrated by way of example.
  • the heat source unit A and the relay unit E are connected via refrigerant pipes 5 (the high-pressure-side connection pipe 106, the low-pressure-side connection pipe 107), and the relay unit E and the use-side units are connected via refrigerant pipes 6 (the connection pipes 133, the connection pipes 134, the connection pipe 135, the connection pipe 136), thereby constituting a single refrigerant circuit system (the refrigeration cycle for air conditioning 1).
  • the heat source unit A is provided with a heat source unit controller 61
  • the relay unit E is provided with a relay unit controller 62.
  • Each of the indoor unit B and the indoor unit C is provided with an indoor unit controller (use-side unit controller) 63
  • each of the hot-water supply units F is provided with a hot-water supply unit controller (use-side unit controller) 64.
  • the heat source unit A is controlled by the heat source unit controller 61
  • the relay unit E is controlled by the relay unit controller 62
  • the indoor unit B and the indoor unit C are controlled by the indoor unit controllers 63
  • the hot-water supply units F are controlled by the hot-water supply unit controllers 64.
  • the heat source unit controller 61 and the relay unit controller 62 are connected to each other via a transmission line 7 so that information can be transferred between them.
  • the relay unit controller 62 and the indoor unit controllers 63 are connected to each other via a transmission line 8 so that information can be transferred between them.
  • the relay unit controller 62 and the hot-water supply unit controllers 64 are connected to each other via the transmission line 8 so that information can be transferred between them.
  • the indoor unit controllers 63 and the hot-water supply unit controllers 64 are connected to remote controllers 65 via transmission lines 9 so that information can be transferred between the indoor unit controllers 63 and the associated remote controllers 65 and between the hot-water supply unit controllers 64 and the associated remote controllers 65.
  • the heat source unit controller 61 is further connected to a heat source unit controller in another refrigerant system (not illustrated) via a transmission line 10.
  • a centralized controller 66 for centralized management of the refrigeration cycle apparatus 100 is also connected to the transmission line 10.
  • Each of the heat source unit controller 61, the relay unit controller 62, the indoor unit controllers 63, the hot-water supply unit controllers 64, the remote controllers 65, and the centralized controller 66 is assigned a unique address, and is configured to obtain the address of a communication partner through manual setting or automatic determination at the time of system start.
  • the heat source unit controller 61 is configured to obtain the operating capacities of all the units connected to the relay unit E, including the indoor unit B, the indoor unit C, and the hot-water supply units F, through communication at the time of system start.
  • Fig. 3 is a schematic diagram schematically illustrating the connection state in a hot-water supply unit F of the refrigeration cycle apparatus 100 according to an embodiment of the present invention.
  • the connection state in a hot-water supply unit F will be described with reference to Fig. 3 .
  • the hot-water supply unit F is provided with the hot-water storage tank 32.
  • the hot-water storage tank 32 is provided with a water supply valve 33 disposed at a water inlet (illustration omitted), a water discharge valve 34 disposed at a water outlet (illustration omitted), a water temperature sensor 35 that detects the temperature of water, hot water, or the like stored in the hot-water storage tank 32, and a water level sensor 36 that detects the amount (water level) of water, hot water, or the like stored in the hot-water storage tank 32.
  • the hot-water supply unit controller 64 is connected to the water temperature sensor 35 and the water level sensor 36, and is configured to be capable of obtaining the temperature of water and the amount of water in the hot-water storage tank 32 on the basis of information transferred from the water temperature sensor 35 and the water level sensor 36.
  • the hot-water supply unit controller 64 is also connected to the water supply valve 33, and is configured to control the opening and closing of the water supply valve 33. That is, the hot-water supply unit controller 64 is configured to open the water supply valve 33 to supply the hot-water storage tank 32 with cold water.
  • the hot-water supply unit controller 64 is further connected to the water discharge valve 34, and is configured to control the opening and closing of the water discharge valve 34. That is, the hot-water supply unit controller 64 is configured to open the water discharge valve 34 so that hot water can be discharged to the outside of the hot-water storage tank 32.
  • Fig. 4 is a flowchart illustrating a flow of a communication/operation process executed by the heat source unit controller 61.
  • the flow of the communication/operation process executed by the heat source unit controller 61 will be described with reference to Fig. 4 .
  • Steps S100 to S106 illustrated in Fig. 4 represent processes executed by the heat source unit controller 61.
  • a description will be given by taking the hot-water supply unit F1 as an example.
  • a user operates the associated remote controller 65 and sets a set temperature of the hot-water supply unit F1.
  • the user can set a binary set temperature.
  • the term binary set temperature refers to a hot-water supply temperature (first set temperature) required for the hot-water supply unit F1 and a temperature (second set temperature) when the hot-water supply unit F1 automatically operates for the purpose of energy saving or continuation of stable operation of the overall system.
  • the second set temperature is set to a value higher than the first set temperature. For example, the user sets 55 degrees C as the first set temperature and 60 degrees C as the second set temperature.
  • the remote controller 65 When a set temperature is input, the remote controller 65 saves the set binary set temperature in a memory, and transmits the set binary set temperature to the associated hot-water supply unit controller 64 via the transmission line 9.
  • the hot-water supply unit controller 64 Upon receipt of the set binary set temperature, the hot-water supply unit controller 64 saves the received binary set temperature in a memory, and transmits the binary set temperature to the relay unit controller 62 via the transmission line 8.
  • the binary set temperature is further transmitted to the centralized controller 66 through the transmission line 8, the transmission line 7, and the transmission line 10.
  • the relay unit controller 62 that has received the binary set temperature also transmits the binary set temperature of each hot-water supply unit F to the heat source unit controller 61 via the transmission line 7.
  • the user When the user do not wish to cause the hot-water supply unit F to automatically operate, they may not set the second set temperature.
  • the user It will also be possible for the user to set the binary set temperature by manipulating the centralized controller 66. In this case, the centralized controller 66 saves a set binary set temperature in a memory, and transmits the set binary set temperature to the associated hot-water supply unit controller 64 through the transmission line 10, the transmission line 7, and the transmission line 8.
  • the hot-water supply unit controller 64 Upon receipt of the set binary set temperature, the hot-water supply unit controller 64 transmits the received binary set temperature to the relay unit controller 62 via the transmission line 8, and also transmits the binary set temperature to the associated remote controller 65 through the transmission line 9.
  • the above communication allows the heat source unit controller 61 to keep information about all the hot-water supply units F connected to the refrigerant circuit as to whether or not automatic operation is possible.
  • the heat source unit controller 61 performs an analysis process for newly received communication (step S101).
  • the communication received here includes the operating/stopping state of all the units connected to the refrigerant circuit, including the indoor units B, the indoor units C, and the hot-water supply units F, and information as to whether or not automatic operation is possible.
  • the heat source unit controller 61 determines whether or not automatic operation is possible (step S102). For example, if one or more of automatically operable hot-water supply units F are stopped or are under automatic operation, it is determined that automatic operation is possible. This is because the apparatus may be used such that even when there is a hot-water supply unit F that is set as a unit possible to perform automatic operation, it may not be permitted to automatically stop when normal operation is started by a user operation.
  • the heat source unit controller 61 analyses the operating capacity, the load state, the system COP, and the like from various kinds of data, such as the operating/stopping state, pressure, temperature, compressor operating frequency, current, and the like of all the units connected to the refrigerant circuit, such as the indoor units B, the indoor units C, and the hot-water supply units F (step S103).
  • the balance of the cooling load, heating load, and the hot water load are determined from the total capacity of an indoor unit B and an indoor unit C with the cooling thermo-on, the total capacity of an indoor unit B and an indoor unit C with the heating thermo-on, and the total capacity of hot-water supply units F with the thermo-on.
  • the heat source unit controller 61 determines whether or not the operating condition can be improved by operating or stopping an automatically operable hot-water supply unit F (step S104). For example, when the cooling load is larger than the heating and hot water loads, if the difference between the cooling load and the heating and hot water loads can be reduced by operating an automatically operable hot-water supply unit F, then it can be determined that the system COP will be increased by allowing the hot-water supply unit F to operate.
  • the motor efficiency of the air conditioning compressor 101 when in the state of the small-capacity heating operation, it can be determined that the motor efficiency of the air conditioning compressor 101 will be improved by allowing an automatically operable hot-water supply unit F to operate, which results in energy saving operation.
  • the number of indoor units C that perform heating operation is increased by manipulation of an user operation and when the heating load becomes large, then, it can be determined that power consumption can be reduced by stopping the hot-water supply unit F that has been allowed to automatically operate.
  • the high-pressure-side pressure can be reduced by operating an automatically operable hot-water supply unit F and that stable operation can be continued. After that, if the high-pressure-side pressure is sufficiently reduced by, for example, change of the number of units operated, it can be determined that power consumption can be reduced by stopping the hot-water supply unit F that has been allowed to automatically operate.
  • the hot-water supply units F to be changed are determined in accordance with a preset priority.
  • the priority may be manually set in advance.
  • the priority may be set in accordance with the intended use such as for a guest room in a hotel, a room for employees, and the like.
  • Another method is also possible in which the priority is set in accordance with the addresses of the hot-water supply unit controllers 64. In this case, the method is made feasible by setting the values of the addresses in ascending order or descending order in accordance with the priority.
  • the priority is determined in accordance with the integrated operating time of each hot-water supply unit F.
  • a hot-water supply unit F with a short integrated operating time is operated with priority to make the integrated operating times uniform, thereby making it possible to avoid the problem of shortening the product life of only a specific hot-water supply unit F.
  • the priority is set in accordance with the value of the difference between the water temperature in the hot-water storage tank 32 of each hot-water supply unit F and a set temperature. In this method, a hot-water supply unit F having a large temperature difference is preferentially operated, thereby enabling continuous operation for a long time.
  • the heat source unit controller 61 transmits information of the hot-water supply unit or units F to be operated and stopped to the relay unit controller 62 (step S105). After the completion of the transmission process, the heat source unit controller 61 performs normal processes such as receiving a sensor input and controlling the actuators (step S106). Meanwhile, also when it is determined that automatic operation is not possible (step S102; N) or when it is determined that the operating condition cannot be improved by operating and stopping an automatically operable hot-water supply unit F (step S104; N), the heat source unit controller 61 performs the normal processes (step S106).
  • the relay unit controller 62 Upon receipt of an automatic operation/stopping command for a hot-water supply unit F from the heat source unit controller 61, the relay unit controller 62 transmits the automatic operation/stopping command to the associated hot-water supply unit controller 64. Upon receipt of notification of a change of the operating condition from an indoor unit controller 63 or a hot-water supply unit controller 64, the relay unit controller 62 transmits the notification of the change in the operating condition to the heat source unit controller 61.
  • the hot-water supply unit controller 64 Upon receipt of an automatic operation/stopping command from the relay unit controller 62, the hot-water supply unit controller 64 changes the operating condition in accordance with the command, and transmits notification of the change of the operating condition to the associated remote controller 65 and the centralized controller 66.
  • the hot-water supply unit controller 64 Upon receipt of a normal operation or stopping command from the remote controller 65 or the centralized controller 66, the hot-water supply unit controller 64 changes the operating condition in accordance with the command, and transmits the change of the operating condition to the relay unit controller 62.
  • the hot-water supply unit controller 64 further identifies the operating condition of the associated hot-water supply unit F as that in normal operation or automatic operation, and holds the operating condition. Further, the hot-water supply unit controller 64 also transmits information of the identified operating conditions of the remote controllers 65 and the centralized controller 66 to the remote controllers 65 and the centralized controller 66.
  • the hot-water supply unit controller 64 operates in order to allow the water temperature to reach the first set temperature, and the hot-water supply unit controller 64 turns off the thermostat when the water temperature has reached the first set temperature. In automatic operation, however, the hot-water supply unit controller 64 maintains the on-state of the thermostat until the water temperature has reached the second set temperature. This is because the hot-water supply unit F is made to be able to continue its operation for a long time for the purpose of energy saving or continuation of stable operation of the overall system.
  • the water supply valve 33 is opened to supply the hot-water storage tank 32 with cold water to reduce the water temperature, and the operation is continued.
  • the hot-water storage tank 32 If the hot-water storage tank 32 is full, the water discharge valve 34 is opened to discharge a certain amount of hot water. Then, the hot-water storage tank 32 is supplied with cold water, and the operation is continued. It is assumed here that the discharge control of cold water can be selected by separately providing a means for determining a priority over continuation of automatic operation.
  • the remote controller 65 and the centralized controller 66 Upon receipt of notification of a change of the automatic operation/stopping condition from the associated hot-water supply unit controller 64, the remote controller 65 and the centralized controller 66 recognize the information, and reflect the information on display. In this case, also regarding display, the normal operation and the automatic operation may be displayed in a distinguishable manner. The purpose is to allow the user to recognize that the automatic operation is in progress and to prevent the user from mistakenly thinking that some other event is in progress such as forgetting to turn off the associated hot-water supply unit F using a remote control (remote controller 65). Additionally, when the associated hot-water supply unit F is operated or stopped by a user, the remote controller 65 and the centralized controller 66 recognize information, reflect the information on display, and transmit the information to the associated hot-water supply unit controller 64.
  • the heat source unit controller 61 includes a means for allowing the hot-water supply unit F to operate is illustrated by way of example. Any other controller may include a means for allowing the hot-water supply unit F to operate.
  • the advantage of the system having a means for allowing the hot-water supply unit F to operate in the heat source unit controller 61 is that the amount of communication can be reduced because the heat source unit A is capable of performing control determination using data of the pressure and temperature thereof, compressor operating frequency, current, and the like.
  • the centralized controller 66 can include a means for operating a hot-water supply unit F. The advantage of this method is that an optimum operating schedule of the hot-water supply unit F can be predicted and created by performing determination using schedule setting information of the overall system which is held in the centralized controller 66.
  • each of the indoor unit controllers 63 can include a means for operating a hot-water supply unit F.
  • control can be performed using a simple algorithm such as operating and stopping a hot-water supply unit F in association with operating and stopping of the indoor unit B and the indoor unit C.
  • a means for operating a hot-water supply unit F can also be provided in the hot-water supply unit controller 64 itself.
  • the advantage of this system is that, due to the autonomous control, the hot-water supply unit F can contribute to energy saving while reducing changes in water temperature.
  • the refrigeration cycle apparatus 100 when the cooling load is larger than the heating load and the hot water load, the refrigeration cycle apparatus 100 operates the hot-water supply device, thereby increasing the system COP and enabling a reduction in running cost while achieving energy saving. Also, the refrigeration cycle apparatus 100 operates the hot-water supply device during the small-capacity heating operation, thereby improving the motor efficiency of the air conditioning compressor 101 and enabling a reduction in running cost while further achieving energy saving. Additionally, the refrigeration cycle apparatus 100 causes the hot-water supply device to operate in the case of the small-capacity overloaded heating operation, thereby reducing the high-pressure-side pressure and allowing for continuation of stable operation.
  • the refrigeration cycle apparatus 100 in which the secondary refrigerant (hot water) of a hot-water supply unit F is used as a heat storing heat medium has been described by way of example.
  • the configuration of the refrigeration cycle apparatus 100 is not limited to this.
  • an air-conditioning apparatus illustrated in Fig. 5 (of the type in which heat is transferred from a direct expansion air conditioner to another secondary refrigerant) can also be used in a similar manner.
  • a case where a hot-water supply unit F is present has been described by way of example.
  • the overall air conditioning loads of the indoor unit B and the indoor unit C may be desirably balanced.
  • Fig. 5 is a refrigerant circuit diagram illustrating another example of the refrigerant circuit configuration of a refrigeration cycle apparatus according to an embodiment of the present invention (hereinafter referred to as a refrigeration cycle apparatus 100A).
  • the refrigerant circuit configuration and operation of the refrigeration cycle apparatus 100A will be described with reference to Fig. 5 .
  • a case where the refrigeration cycle apparatus 100A is an air-conditioning apparatus capable of simultaneously supplying a cooling load and a heating load (or a hot water load) by utilizing a refrigeration cycle in which a refrigerant (heat-source refrigerant) is circulated is illustrated by way of example.
  • the difference between Fig. 5 and Fig. 1 will be primarily described, and, in Fig. 5 , the same portions as those in Fig. 1 are assigned the same numerals and a description thereof is omitted.
  • the heat source unit A and a relay unit (hereinafter referred to as the relay unit E1) are connected to each other by a refrigerant pipe 5 (the high-pressure-side connection pipe 106, the low-pressure-side connection pipe 107) via a heat exchanger related to heat medium 71a and a heat exchanger related to heat medium 71b which are included in the relay unit E1.
  • the relay unit E1 and an indoor unit (hereinafter referred to as the indoor unit B1) are also connected to each other by a refrigerant pipe 6 via the heat exchanger related to heat medium 71a and the heat exchanger related to heat medium 71b.
  • all the illustrated indoor units are referred to as indoor units B1 for convenience of illustration.
  • Each of the indoor units B1 has mounted therein an indoor heat exchanger 118. That is, each of the indoor units B1 is different from the indoor unit B in that the air conditioning expansion device 117 is not mounted.
  • the indoor heat exchangers 118 are designed to be connected to heat medium flow control devices 75 and second heat medium flow switching devices 76 in the relay unit E1 by refrigerant pipes 6.
  • Fig. 5 a case where four indoor units B1 are connected to the relay unit E1 is illustrated by way of example. However, the number of indoor units B1 connected is not limited to four.
  • the relay unit E1 has mounted therein the two heat exchangers related to heat medium 71, two expansion devices 72, two on-off devices 73, two second refrigerant flow switching devices 74, two pumps 80, four first heat medium flow switching devices 77, the four second heat medium flow switching devices 76, and the four heat medium flow control devices 75.
  • Each of the two heat exchangers related to heat medium 71 functions as a condenser (radiator) or an evaporator, and is configured to exchange heat between the heat-source-side refrigerant and the heat medium to transfer cooling energy or heating energy generated by the heat source unit A and stored in the heat-source-side refrigerant to the heat medium.
  • the heat exchanger related to heat medium 71a is provided between the expansion device 72a and a second refrigerant flow switching device 74a, and serve to cool the heat medium in a cooling/heating combined operation mode.
  • the heat exchanger related to heat medium 71b is provided between the expansion device 72b and a second refrigerant flow switching device 74b, and serves to heat the heat medium in the cooling/heating combined operation mode.
  • Each of the two expansion devices 72 has the function of a pressure reducing valve or an expansion valve, and is configured to reduce the pressure of the heat-source-side refrigerant to cause the heat-source-side refrigerant to expand.
  • the expansion device 72a is provided upstream from the heat exchanger related to heat medium 71a in the direction of the flow of the heat-source-side refrigerant during the cooling operation.
  • the expansion device 72b is provided upstream from the heat exchanger related to heat medium 71b in the direction of the flow of the heat-source-side refrigerant during the cooling operation.
  • Each of the two expansion devices 72 may be constituted by a mechanism whose opening degree is variably controllable, such as an electronic expansion valve.
  • the two on-off devices 73 are constituted by two-way valves or the like, and are configured to open and close the refrigerant pipe 5.
  • the on-off device 73a is provided on the heat-source-side refrigerant inlet side of the refrigerant pipe 5.
  • the on-off device 73b is provided in a pipe that connects the heat-source-side refrigerant inlet and outlet sides of the refrigerant pipe 5.
  • Each of the two second refrigerant flow switching devices 74 (the second refrigerant flow switching device 74a and the second refrigerant flow switching device 74b) is constituted by a four-way valve or the like, and is configured to switch the flow of the heat-source-side refrigerant in accordance with the operation mode.
  • the second refrigerant flow switching device 74a is provided downstream from the heat exchanger related to heat medium 71a in the direction of the flow of the heat-source-side refrigerant during the cooling operation.
  • the second refrigerant flow switching device 74b is provided downstream from the heat exchanger related to heat medium 71b in the direction of the flow of the heat-source-side refrigerant during the cooling only operation.
  • the two pumps 80 (a pump 80a and a pump 80b) are configured to circulate the heat medium passing through the refrigerant pipes 6.
  • the pump 80a is provided in the refrigerant pipe 6 between the heat exchanger related to heat medium 71a and the second heat medium flow switching devices 76.
  • the pump 80b is provided in the refrigerant pipe 6 between the heat exchanger related to heat medium 71b and the second heat medium flow switching devices 76.
  • the two pumps 80 may be constituted by, for example, pumps whose capacity can be controlled or the like.
  • Each of the four first heat medium flow switching devices 77 is constituted by a three-way valve or the like, and is configured to switch the flow path of the heat medium.
  • the first heat medium flow switching devices 77 the number of which corresponds to the number of indoor units B1 installed (here, four), are provided.
  • one of the three ways is connected to the associated heat exchanger related to heat medium 71a
  • another of the three ways is connected to the associated heat exchanger related to heat medium 71b
  • the other of the three ways is connected to the associated heat medium flow control device 75.
  • the first heat medium flow switching devices 77 are provided on the outlet side of the heat medium flow paths extending from the indoor heat exchangers 118.
  • Each of the four second heat medium flow switching devices 76 is constituted by a three-way valve or the like, and is configured to switch the flow path of the heat medium.
  • the second heat medium flow switching devices 76 the number of which corresponds to the number of indoor units B installed (here, four), are provided.
  • one of the three ways is connected to the associated heat exchanger related to heat medium 71a
  • another of the three ways is connected to the associated heat exchanger related to heat medium 71b
  • the other of the three ways is connected to the associated indoor heat exchanger 118
  • the second heat medium flow switching devices 76 are provided on the inlet side of the heat medium flow paths extending from the indoor heat exchangers 118.
  • Each of the four heat medium flow control devices 75 is constituted by a two-way valve or the like using, for example, a stepping motor, and is configured to make changeable the opening degree of the associated refrigerant pipe 6 serving as a heat medium flow path to control the flow rate of the heat medium.
  • the heat medium flow control devices 75 the number of which corresponds to the number of indoor units B1 installed (here, four), are provided.
  • one way is connected to the associated indoor heat exchanger 118 and the other way is connected to the associated first heat medium flow switching device 77, and the heat medium flow control devices 75 are provided on the outlet side of the heat medium flow paths extending from the indoor heat exchangers 118.
  • the heat medium flow control devices 75 may be provided on the inlet side of the heat medium flow paths extending from the indoor heat exchangers 118.
  • the heat source unit A and the relay unit E1 are connected to each other via the heat exchanger related to heat medium 71a and the heat exchanger related to heat medium 71b which are provided in the relay unit E1, and the relay unit E1 and the indoor units B1 are also connected to each other via the heat exchanger related to heat medium 71a and the heat exchanger related to heat medium 71b.
  • the refrigeration cycle apparatus 100A is configured such that the heat-source-side refrigerant circulating in the refrigeration cycle for air conditioning 1 and the heat medium circulating in the a heat medium cycle (for example, the refrigeration cycle for hot-water supply 2 described with reference to Fig. 1 ) exchange heat in the heat exchanger related to heat medium 71a and the heat exchanger related to heat medium 71b.
  • the refrigeration cycle apparatus 100A having the above configuration increases the system COP by causing the hot-water supply device to operate when the cooling load is larger than the heating load (or the hot water load), and enables a reduction in running cost while achieving energy saving.
  • the refrigeration cycle apparatus 100A further improves the motor efficiency of the air conditioning compressor 101 by causing the heating device (or the hot-water supply device) to operate during the small-capacity heating operation, and enables a reduction in running cost while further achieving energy saving. Additionally, in the case of the small-capacity overloaded heating operation, the refrigeration cycle apparatus 100A causes the heating device (or the hot-water supply device) to operate, thereby reducing the high-pressure-side pressure and allowing for continuation of stable operation.
  • 1 refrigeration cycle for air conditioning 2 refrigeration cycle for hot-water supply, 3 hot-water supply device, 5 refrigerant pipe, 6 refrigerant pipe, 7 transmission line, 8 transmission line, 9 transmission line, 10 transmission line, 21 hot-water supply compressor, 22 hot-water supply expansion device, 31 water circulation pump, 32 hot-water storage tank, 33 water supply valve, 34 water discharge valve, 35 water temperature sensor, 36 water level sensor, 41 refrigerant heat exchanger, 45 refrigerant pipe, 51 refrigerant heat exchanger, 61 heat source unit controller, 62 relay unit controller, 63 indoor unit controller, 64 hot-water supply unit controller, 65 remote controller, 66 centralized controller, 71 heat exchanger related to heat medium, 71a heat exchanger related to heat medium, 71b heat exchanger related to heat medium, 72 expansion device, 72a expansion device, 72b expansion device, 73 on-off device, 73a on-off device, 73b on-off device, 74 refrigerant flow switching device, 74a refrigerant flow switching device, 74b

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Claims (7)

  1. Appareil de cycle de réfrigération (100) comprenant :
    au moins une unité source de chaleur (A) à l'intérieur de laquelle sont montés au moins un compresseur de climatisation (101) et un échangeur de chaleur du côté source de chaleur (103) ;
    une pluralité d'unités du côté utilisation (B, C, D), à l'intérieur de chacune d'elles est monté au moins un échangeur de chaleur du côté utilisation (118), les unités du côté utilisation étant fonctionnelles de manière automatique ; et
    au moins une unité relais (E) qui est disposée entre l'unité source de chaleur (A) et les unités du côté utilisation, et qui transfère l'énergie de chauffage ou l'énergie de refroidissement générée par l'unité du côté de source de chaleur, aux unités du côté utilisation ;
    dans lequel l'unité source de chaleur (A) est dotée d'un contrôleur d'unité source de chaleur (61) qui commande le fonctionnement de la pluralité d'unités du côté utilisation ;
    caractérisé en ce que :
    dans le cas où l'une au moins de la pluralité d'unités du côté utilisation est arrêtée ou est en fonctionnement automatique, parmi la pluralité d'unités du côté utilisation fonctionnelles de manière automatique (B, C, D), en utilisant la ou les unités de la pluralité d'unités du côté utilisation qui sont arrêtées ou qui sont en fonctionnement automatique parmi la pluralité d'unités du côté utilisation fonctionnelles de manière automatique (B, C, D), la pluralité d'unités du côté utilisation sont actionnées de telle sorte qu'une charge de refroidissement thermique et qu'une charge de chauffage thermique à exécuter par la pluralité d'unités du côté utilisation, soient équilibrées ; et
    en ce que :
    quand une charge totale sur une unité du côté utilisation qui exécute une opération de charge de refroidissement de chaleur, est supérieure à une charge totale sur une unité du côté utilisation qui exécute une opération de charge de chauffage thermique,
    une unité du côté utilisation qui est arrêtée ou qui est en fonctionnement automatique parmi la pluralité d'unités du côté utilisation (B, C, D), exécute l'opération de charge de chauffage thermique.
  2. Appareil de cycle de réfrigération (100) selon la revendication 1, dans lequel :
    lorsque la charge de chauffage thermique est petite et sans charge de refroidissement thermique, et lorsque la fréquence de fonctionnement du compresseur est inférieure à une valeur prédéterminée, ou lorsque la température extérieure et la température intérieure sont supérieures à une valeur prédéterminée, et lorsque la pression du côté pression élevée est supérieure à une valeur prédéterminée ;
    on détermine que la charge totale sur une unité du côté utilisation qui exécute l'opération de charge de refroidissement thermique, est supérieure une charge totale sur une unité du côté utilisation qui exécute l'opération de charge de chauffage thermique.
  3. Appareil de cycle de réfrigération (100) selon la revendication 1 ou la revendication 2, dans lequel :
    l'opération de charge de chauffage thermique à exécuter par une unité du côté utilisation, est une opération de chauffage ou une opération de fourniture d'eau chaude ; et
    l'opération de charge de refroidissement thermique à exécuter par une unité du côté utilisation, est une opération de refroidissement.
  4. Appareil de cycle de réfrigération (100) selon l'une quelconque des revendications 1 à 3, dans lequel :
    deux températures peuvent être fixées pour chacune des unités du côté utilisation (B, C, D), les deux températures comprenant une première température fixée requise par l'unité du côté utilisation, et une seconde température fixée lorsque l'unité du côté utilisation est actionnée de manière automatique ; et
    on détermine qu'une unité du côté utilisation qui présente la seconde température fixée, est une unité du côté utilisation fonctionnelle de manière automatique.
  5. Appareil de cycle de réfrigération (100) selon l'une quelconque des revendications 1 à 4, dans lequel :
    quand il y a une pluralité d'unités du côté utilisation (B, C, D) qui n'exécutent ni opération de charge de chauffage thermique, ni opération de charge de refroidissement thermique,
    une unité du côté utilisation parmi les unités du côté utilisation qui n'exécutent aucune opération, exécute l'opération de charge de chauffage thermique selon une priorité préréglée.
  6. Appareil de cycle de réfrigération (100) selon l'une quelconque des revendications 3 à 5, dans lequel :
    quand aucune unité du côté utilisation n'exécute ni opération de charge de chauffage thermique ni opération de charge de refroidissement thermique, l'opération de charge de chauffage thermique est poursuivie par une fourniture d'eau froide.
  7. Procédé de transfert d'informations appliqué à l'appareil de cycle de réfrigération (100) selon l'une quelconque des revendications 1 à 6, dans lequel :
    l'unité source de chaleur (A) est dotée d'un contrôleur d'unité source de chaleur (61), l'unité relais (E) est dotée d'un contrôleur d'unité relais (62), chacune des unités du côté utilisation (B, C, D) est dotée d'un contrôleur d'unité du côté utilisation (63) ; et
    le transfert d'informations en provenance de chacun des contrôleurs, permet à n'importe lequel des contrôleurs de déterminer l'équilibre de charge entre la pluralité d'unités du côté utilisation (B, C, D).
EP09851418.5A 2009-11-18 2009-11-18 Dispositif à cycle de réfrigération et procédé de propagation d'informations adapté à celui-ci Not-in-force EP2503266B1 (fr)

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EP2503266A1 (fr) 2012-09-26
JPWO2011061792A1 (ja) 2013-04-04
US20120222440A1 (en) 2012-09-06
JP5642085B2 (ja) 2014-12-17
EP2503266A4 (fr) 2016-10-05
WO2011061792A1 (fr) 2011-05-26
CN102695929B (zh) 2014-07-30
CN102695929A (zh) 2012-09-26

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