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WO2010082324A1 - Système complexe de climatisation et d'alimentation en eau chaude - Google Patents

Système complexe de climatisation et d'alimentation en eau chaude Download PDF

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Publication number
WO2010082324A1
WO2010082324A1 PCT/JP2009/050407 JP2009050407W WO2010082324A1 WO 2010082324 A1 WO2010082324 A1 WO 2010082324A1 JP 2009050407 W JP2009050407 W JP 2009050407W WO 2010082324 A1 WO2010082324 A1 WO 2010082324A1
Authority
WO
WIPO (PCT)
Prior art keywords
hot water
refrigerant
water supply
heat exchanger
heat medium
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.)
Ceased
Application number
PCT/JP2009/050407
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English (en)
Japanese (ja)
Inventor
宏典 薮内
純一 亀山
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
Priority to EP09838294.8A priority Critical patent/EP2378223B1/fr
Priority to PCT/JP2009/050407 priority patent/WO2010082324A1/fr
Priority to JP2010546506A priority patent/JP5264936B2/ja
Publication of WO2010082324A1 publication Critical patent/WO2010082324A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • 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
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—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
    • 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 an air-conditioning and hot-water supply complex system equipped with a heat pump cycle and capable of simultaneously providing a cooling load, a heating load and a hot water supply load.
  • the first compressor, the refrigerant distributor, the first heat exchanger, the second heat exchanger, the first expansion device, the outdoor heat exchanger, the four-way valve, and the first compressor are connected in this order.
  • the four-way valve, the indoor heat exchanger, and the second expansion device are interposed in this order from the refrigerant distribution device, and connected between the second heat exchanger and the first expansion device, and the first refrigerant
  • a low-stage refrigerant circuit through which the second refrigerant flows, a second compressor, a condenser, a third expansion device, the first heat exchanger, and the second compressor are connected in this order, and the second refrigerant flows.
  • a “heat pump type hot water supply apparatus including a stage-side refrigerant circuit, the second heat exchanger, and the condenser connected in this order, and a hot water supply path through which hot water flows through (for example, Patent Document 2). reference).
  • JP-A-11-270920 page 3-4, FIG. 1
  • Japanese Patent Laid-Open No. 4-263758 page 2-3, FIG. 1
  • the multi-function heat pump system described in Patent Document 1 provides a cooling load, a heating load, and a hot water supply load simultaneously by a single refrigeration cycle, that is, one refrigeration cycle.
  • a single refrigeration cycle that is, one refrigeration cycle.
  • the temperature of the heat dissipation process for heating water and the temperature of the heat dissipation process for heating are almost the same, so that a high temperature hot water supply load must be covered during cooling operation.
  • the compressor must continue to operate until the heat source is raised, which has a problem of poor operating efficiency.
  • the heat pump type hot water supply apparatus described in Patent Document 2 provides a cooling load, a heating load, and a hot water supply load simultaneously by two refrigeration cycles, that is, two refrigeration cycles.
  • the refrigerant circuit that performs air conditioning in the indoor unit and the refrigerant circuit that performs hot water supply are handled differently, and a hot water supply function cannot simply be added as an alternative to the indoor unit. There is a problem that it cannot be easily introduced into an existing air conditioner.
  • the present invention has been made to solve the above-described problems, and can simultaneously process a cooling load, a heating load, and a high-temperature hot water supply load, can supply a stable heat source throughout the year, and can quickly start up at startup. It aims at providing the air-conditioning hot-water supply complex system which makes it possible to do.
  • an air conditioning compressor, a flow path switching unit, an outdoor heat exchanger, an indoor heat exchanger, and an air conditioning throttle unit are connected in series and connected in series.
  • the refrigerant-refrigerant heat exchanger and the hot water supply heat source throttle means include a first refrigerant circuit connected in parallel to the indoor heat exchanger and the air conditioning throttle means, and circulates the air-conditioning refrigerant in the first refrigerant circuit.
  • An air conditioning refrigeration cycle a hot water supply compressor, a heat medium-refrigerant heat exchanger, hot water supply throttle means, and a second refrigerant circuit in which the refrigerant-refrigerant heat exchanger is connected in series
  • the air-conditioning refrigeration cycle and the hot-water supply refrigeration cycle are cascade-connected in the refrigerant-refrigerant heat exchanger so that the air-conditioning refrigerant and the hot-water supply refrigerant perform heat exchange, and the hot-water supply
  • the refrigeration cycle for hot water and the hot water supply load are cascade-connected in the heat medium-refrigerant heat exchanger so that the hot water supply refrigerant and the water exchange heat
  • the combined air conditioning and hot water supply system it is possible to simultaneously or selectively perform the cooling operation, the heating operation, and the hot water supply operation in combination with the air conditioning load and the hot water supply load without configuring a complicated circuit.
  • By improving the start-up (particularly the hot water supply compressor), highly efficient operation is possible.
  • FIG. 1 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration (particularly, a refrigerant circuit configuration during heating-main operation) of an air-conditioning and hot water supply combined system 100 according to an embodiment of the present invention. Based on FIG. 1, the refrigerant circuit configuration of the combined air-conditioning and hot water supply system 100, particularly the refrigerant circuit configuration during heating-main operation will be described.
  • This air conditioning and hot water supply complex system 100 is installed in a building, a condominium, etc., and can supply a cooling load, a heating load, and a hot water supply load simultaneously by using a refrigeration cycle (heat pump cycle) that circulates refrigerant (air conditioning refrigerant). is there.
  • a refrigeration cycle heat pump cycle
  • refrigerant air conditioning refrigerant
  • An air conditioning and hot water supply combined system 100 includes an air conditioning refrigeration cycle 1, a hot water supply refrigeration cycle 2, and a hot water supply load 3, and includes an air conditioning refrigeration cycle 1 and a hot water supply refrigeration cycle 2.
  • Is a refrigerant-refrigerant heat exchanger 41, and the hot water supply refrigeration cycle 2 and the hot water supply load 3 are heat medium-refrigerant heat exchangers 51, and are configured to exchange heat without mutual refrigerant or water mixing.
  • the load on the cooling indoor unit B is smaller than the total load on the heating indoor unit C and the hot water supply heat source circuit D, and the outdoor heat exchanger 103 serves as an evaporator.
  • the state of the cycle when working (for convenience, referred to as heating main operation) is shown.
  • the air-conditioning refrigeration cycle 1 includes a heat source unit A, a cooling indoor unit B in charge of a cooling load, a heating indoor unit C in charge of a heating load, a hot water supply heat source circuit D serving as a heat source of the hot water supply refrigeration cycle 2, And a repeater E.
  • the cooling indoor unit B, the heating indoor unit C, and the hot water supply heat source circuit D are connected and mounted in parallel to the heat source unit A.
  • the relay machine E installed between the heat source unit A, the cooling indoor unit B, the heating indoor unit C, and the hot water supply heat source circuit D switches the flow of the refrigerant, so that the cooling indoor unit B, the heating indoor unit The functions as C and hot water supply heat source circuit D are exhibited.
  • the heat source machine A is configured by connecting an air conditioning compressor 101, a four-way valve 102 as a flow path switching unit, an outdoor heat exchanger 103, and an accumulator 104 in series.
  • the cooling indoor unit B, the heating indoor unit C, and the hot water supply heat source circuit D have a function of supplying cold heat.
  • a blower such as a fan for supplying air to the outdoor heat exchanger 103 may be provided in the vicinity of the outdoor heat exchanger 103.
  • the flow of the air-conditioning refrigerant is allowed only in a predetermined direction (the direction from the heat source unit A to the relay unit E) in the high-pressure side connection pipe 106 between the outdoor heat exchanger 103 and the relay unit E.
  • the reverse check valve 105a that allows the flow of the air-conditioning refrigerant only in a predetermined direction (direction from the relay machine E to the heat source machine A) in the low-pressure side connection pipe 107 between the four-way valve 102 and the relay machine E. Stop valves 105b are provided respectively.
  • the high-pressure side connection pipe 106 and the low-pressure side connection pipe 107 are opposite to the first connection pipe 130 that connects the upstream side of the check valve 105a and the upstream side of the check valve 105b, and the downstream side of the check valve 105a.
  • the second connection pipe 131 is connected to the downstream side of the stop valve 105b. That is, the connection part a between the high-pressure side connection pipe 106 and the first connection pipe 130 is upstream of the connection part b between the high-pressure side connection pipe 106 and the second connection pipe 131 across the check valve 105a.
  • the connection part c between the low-pressure side connection pipe 107 and the first connection pipe 130 is also upstream of the connection part d between the low-pressure side connection pipe 107 and the second connection pipe 131 across the check valve 105b. Yes.
  • the first connection pipe 130 is provided with a check valve 105 c that allows the air-conditioning refrigerant to flow only in the direction from the low-pressure side connection pipe 107 to the high-pressure side connection pipe 106.
  • the second connection pipe 131 is also provided with a check valve 105 d that allows the air-conditioning refrigerant to flow only in the direction from the low-pressure side connection pipe 107 to the high-pressure side connection pipe 106.
  • the check valve 105a and the check valve 105b are in a closed state (shown in black), the check valve 105b and the check valve 105c. Is open (shown in white).
  • the air-conditioning compressor 101 sucks air-conditioning refrigerant and compresses the air-conditioning refrigerant to a high temperature and high pressure state.
  • the four-way valve 102 switches the flow of the air conditioning refrigerant.
  • the outdoor heat exchanger 103 functions as an evaporator or a radiator (condenser), performs heat exchange between air supplied from a blower (not shown) and the air conditioning refrigerant, and converts the air conditioning refrigerant into evaporated gas or Condensed liquid.
  • the accumulator 104 is disposed between the four-way valve 102 and the air-conditioning compressor 101 during heating-main operation, and stores excess air-conditioning refrigerant.
  • the accumulator 104 may be any container that can store excess air-conditioning refrigerant.
  • the cooling indoor unit B and the heating indoor unit C are mounted with an air conditioning throttle means 117 and an indoor heat exchanger 118 connected in series. Further, in the cooling indoor unit B and the heating indoor unit C, an example is shown in which two air conditioning throttle means 117 and two indoor heat exchangers 118 are mounted in parallel.
  • the cooling indoor unit B receives a supply of cold from the heat source unit A and takes charge of the cooling load
  • the heating indoor unit C has a function of receiving the supply of cold heat from the heat source unit A and taking charge of the heating load. Yes.
  • connection pipe 133 the connection pipe connected from the relay E to the indoor heat exchanger 118
  • connection pipe 134 the connection pipe connected from the relay E to the air conditioning throttle means 117
  • the air conditioning throttle means 117 functions as a pressure reducing valve or an expansion valve, and decompresses and expands the air conditioning refrigerant.
  • the air-conditioning throttle means 117 may be constituted by a controllable opening degree, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like.
  • the indoor heat exchanger 118 functions as a radiator (condenser) or an evaporator, and performs heat exchange between air supplied from an air blower (not shown) and the air conditioning refrigerant to condense or liquefy the air conditioning refrigerant. Evaporative gasification.
  • the air conditioning throttle means 117 and the indoor heat exchanger 118 are connected in series.
  • the hot water supply heat source circuit D includes a hot water supply heat source throttling means 119 and a refrigerant-refrigerant heat exchanger 41 connected in series, and the cold heat from the heat source unit A is transferred to the refrigerant-refrigerant heat exchanger 41. It has the function to supply to the hot water supply refrigeration cycle 2 via the. That is, the air-conditioning refrigeration cycle 1 and the hot water supply refrigeration cycle 2 are cascade-connected by the refrigerant-refrigerant heat exchanger 41.
  • the connecting pipe connecting the relay E to the refrigerant-refrigerant heat exchanger 41 is connected to the connecting pipe 135, and the connecting pipe connecting the relay E to the hot water supply heat source throttle means 119 is connected to the connecting pipe. It shall be described as 136.
  • the hot water supply heat source throttling means 119 functions as a pressure reducing valve or an expansion valve, like the air conditioning throttling means 117, and decompresses and expands the air conditioning refrigerant.
  • the hot water supply heat source throttling means 119 is preferably constituted by a controllable opening degree, such as a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary.
  • the refrigerant-refrigerant heat exchanger 41 functions as a radiator (condenser) and an evaporator, and serves as a hot water supply refrigerant that circulates through the refrigeration cycle of the hot water supply refrigeration cycle 2 and an air conditioner that circulates through the refrigeration cycle of the air conditioning refrigeration cycle 1. Heat exchange is performed with the refrigerant for use.
  • the relay unit E has a function of connecting each of the cooling indoor unit B, the heating indoor unit C, and the hot water supply heat source circuit D to the heat source unit A, and also has the valve means 109a or the valve means 109b of the first distribution unit 109. Is selectively opened or closed to determine whether the indoor heat exchanger 118 is a radiator or an evaporator, and whether the refrigerant-refrigerant heat exchanger 41 is a chiller or a water heater. It has a function to do.
  • the relay E includes a gas-liquid separator 108, a first distributor 109, a second distributor 110, a first internal heat exchanger 111, a first relay throttle means 112, and a second internal heat.
  • the exchanger 113 and the second relay stop means 114 are configured.
  • connection pipe 133 and the connection pipe 135 are branched into two, one (the connection pipe 133b and the connection pipe 135b) is connected to the low-pressure side connection pipe 107, and the other (the connection pipe 133a and the connection pipe).
  • the pipe 135a) is connected to a connection pipe (referred to as a connection pipe 132) connected to the gas-liquid separator 108.
  • the valve means 109a that is controlled to open / close the connection pipe 133a and the connection pipe 135a so as not to conduct the refrigerant is controlled to open / close to the connection pipe 133b and the connection pipe 135b and conducts the refrigerant.
  • Valve means 109b that may or may not be provided is provided.
  • the open / closed states of the valve means 109a and the valve means 109b are represented by white (open state) and black (closed state).
  • connection pipe 134 and the connection pipe 136 are branched into two, one (the connection pipe 134a and the connection pipe 136a) is connected at the first meeting part 115, and the other (the connection pipe 134b and the connection pipe).
  • a pipe 136b) is connected at the second meeting part 116.
  • the check valve 110a that allows only one of the refrigerant to flow in the connecting pipe 134a and the connecting pipe 136a is reverse to allow only one of the refrigerant to flow in the connecting pipe 134b and the connecting pipe 136b.
  • a stop valve 110b is provided.
  • the open / closed states of the check valve 110a and the check valve 110b are indicated by white (open state) and black (closed state).
  • the first meeting unit 115 is connected from the second distribution unit 110 to the gas-liquid separator 108 via the first relay squeezing means 112 and the first internal heat exchanger 111.
  • the second meeting unit 116 branches between the second distribution unit 110 and the second internal heat exchanger 113, one of which is for the second distribution unit 110 and the first relay device via the second internal heat exchanger 113.
  • the second meeting section 116a is connected to the first meeting section 115 between the throttling means 112, and the other (second meeting section 116a) is connected to the second relay throttling means 114, the second internal heat exchanger 113, and the first internal heat exchanger 111.
  • the gas-liquid separator 108 separates the air-conditioning 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 of which is connected to the valve means 109 a of the first distribution unit 109, and the other.
  • the first distributor 115 is connected to the second distributor 110.
  • the first distribution unit 109 has a function of allowing the air conditioning refrigerant to flow into the indoor heat exchanger 118 and the refrigerant-refrigerant heat exchanger 41 by selectively opening or closing either the valve means 109a or the valve means 109b. Yes.
  • the 2nd distribution part 110 has a function which permits the flow of the refrigerant for air-conditioning to either one by check valve 110a and check valve 110b.
  • the first internal heat exchanger 111 is provided in the first meeting portion 115 between the gas-liquid separator 108 and the first relay throttle means 112, and is used for air conditioning in which the first meeting portion 115 is conducted. Heat exchange is performed between the refrigerant and the air-conditioning refrigerant that is conducted through the second meeting part 116a from which the second meeting part 116 is branched.
  • the first repeater throttle means 112 is provided in the first meeting section 115 between the first internal heat exchanger 111 and the second distribution section 110, and decompresses and expands the air-conditioning refrigerant. .
  • the first repeater throttle means 112 may be configured with a variable opening degree controllable means, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like.
  • the second internal heat exchanger 113 is provided in the second meeting part 116, and includes an air conditioning refrigerant that is conducted through the second meeting part 116, and a second meeting part 116a from which the second meeting part 116 is branched. Heat exchange is performed with the air-conditioning refrigerant that is conducted.
  • the second relay throttling means 114 is provided in the second meeting section 116 between the second internal heat exchanger 113 and the second distribution section 110, functions as a pressure reducing valve and an expansion valve, and is an air conditioning refrigerant. Is expanded under reduced pressure.
  • the second relay unit throttle unit 114 can be controlled to have a variable opening, for example, a precise flow rate control unit using an electronic expansion valve, or a low cost such as a capillary tube.
  • the refrigerant flow rate adjusting means may be used.
  • the air-conditioning refrigeration cycle 1 includes the air-conditioning compressor 101, the four-way valve 102, the indoor heat exchanger 118, the air-conditioning throttle means 117, and the outdoor heat exchanger 103 connected in series, and the air-conditioning compression cycle.
  • Machine 101, four-way valve 102, refrigerant-refrigerant heat exchanger 41, hot water supply heat source throttling means 119, and outdoor heat exchanger 103 are connected in series, and the indoor heat exchanger 118 and refrigerant-refrigerant are connected via relay E. This is established by connecting the heat exchanger 41 in parallel to form a first refrigerant circuit, and circulating the air-conditioning refrigerant in the first refrigerant circuit.
  • the air conditioning compressor 101 is not particularly limited as long as it can compress the sucked refrigerant into a high pressure state.
  • the air-conditioning compressor 101 can be configured using various types such as reciprocating, rotary, scroll, or screw.
  • the air-conditioning compressor 101 may be configured as a type in which the rotational speed can be variably controlled by an inverter, or may be configured as a type in which the rotational speed is fixed.
  • the type of refrigerant circulating in the air-conditioning refrigeration cycle 1 is not particularly limited.
  • natural refrigerants such as carbon dioxide (CO 2 ), hydrocarbons, and helium, and alternatives that do not contain chlorine such as HFC410A, HFC407C, and HFC404A
  • HFC410A, HFC407C, and HFC404A Either a refrigerant or a fluorocarbon refrigerant such as R22 or R134a used in existing products may be used.
  • the air-conditioning refrigerant heated to a high temperature and high pressure by the air-conditioning compressor 101 is discharged from the air-conditioning compressor 101, passes through the four-way valve 102, passes through the check valve 105 c, and enters the high-pressure side connection pipe 106. It is guided and flows into the gas-liquid separator 108 of the relay E in the superheated gas state.
  • the superheated gas-conditioning refrigerant flowing into the gas-liquid separator 108 is distributed to a circuit in which the valve means 109a of the first distribution unit 109 is open.
  • the refrigerant for air conditioning in the superheated gas state flows into the heating indoor unit C and the hot water supply heat source circuit D.
  • the air-conditioning refrigerant flowing into the heating indoor unit C dissipates heat in the indoor heat exchanger 118 (that is, warms the room air), is depressurized by the air-conditioning throttle means 117, and joins at the first meeting unit 115.
  • the air-conditioning refrigerant that has flowed into the hot water supply heat source circuit D dissipates heat in the refrigerant-refrigerant heat exchanger 41 (that is, gives heat to the hot water supply refrigeration cycle 2), and is depressurized by the hot water supply heat source throttling means 119.
  • the air-conditioning refrigerant that has flowed out of the indoor unit C merges at the first meeting unit 115.
  • a part of the air-conditioning refrigerant in the superheated gas state that has flowed into the gas-liquid separator 108 is the air-conditioning refrigerant expanded to low temperature and low pressure by the second relay expansion means 114 in the first internal heat exchanger 111.
  • the degree of supercooling is obtained by heat exchange.
  • the air-conditioning refrigerant used for air-conditioning flows into the indoor heat exchanger 118 or refrigerant-refrigerant heat exchange. And the first meeting part 115 merge. It should be noted that a part of the superheated gas conditioning refrigerant that passes through the first repeater throttle means 112 may be eliminated by fully closing the first repeater throttle means 112. Thereafter, the second internal heat exchanger 113 performs heat exchange with the air-conditioning refrigerant expanded to low temperature and low pressure by the second relay throttle unit 114 to obtain a degree of supercooling. This refrigerant for air conditioning is distributed to the second meeting part 116 side and the second relay unit throttle means 114 side.
  • the air-conditioning refrigerant that conducts through the second meeting portion 116 is distributed to a circuit in which the valve means 109b is open.
  • the air-conditioning refrigerant that conducts through the second meeting portion 116 flows into the cooling indoor unit B, is expanded to low temperature and low pressure by the air-conditioning throttle means 117, is evaporated by the indoor heat exchanger 118, and the valve means 109 b. After that, the low pressure side connecting pipe 107 joins.
  • the air-conditioning refrigerant that has passed through the second repeater throttle means 114 evaporates by exchanging heat in the second internal heat exchanger 113 and the first internal heat exchanger 111, and in the cooling chamber through the low-pressure side connection pipe 107.
  • the air-conditioning refrigerant merged in the low-pressure side connection pipe 107 is led to the outdoor heat exchanger 103 through the check valve 105d, and depending on the operating conditions, the remaining liquid refrigerant is evaporated, and the four-way valve 102, accumulator Return to the air-conditioning compressor 101 via the radiator 104.
  • the hot water supply refrigeration cycle 2 includes a hot water supply compressor 21, a heat medium-refrigerant heat exchanger 51, hot water supply throttle means 22, and a refrigerant-refrigerant heat exchanger 41. That is, the hot water supply refrigeration cycle 2 includes a hot water supply compressor 21, a heat medium-refrigerant heat exchanger 51, a hot water supply throttle means 22, and a refrigerant-refrigerant heat exchanger 41 connected in series by the refrigerant pipe 45. This is established by constituting a two refrigerant circuit and circulating a hot water supply refrigerant in the second refrigerant circuit. The operation of the hot water supply refrigeration cycle 2 does not differ depending on the operating state of the air conditioning refrigeration cycle 1, that is, whether the cooling main operation is being executed or the heating main operation is being executed.
  • the hot water supply compressor 21 sucks in the hot water supply refrigerant and compresses the hot water supply refrigerant to a high temperature and high pressure state.
  • the hot water supply compressor 21 may be configured as a type in which the rotation speed can be variably controlled by an inverter, or may be configured as a type in which the rotation speed is fixed. Further, the hot water supply compressor 21 is not particularly limited as long as it can compress the sucked refrigerant into a high pressure state.
  • the hot water supply compressor 21 can be configured using various types such as reciprocating, rotary, scroll, or screw.
  • the heat medium-refrigerant heat exchanger 51 performs heat exchange between a heat medium (fluid such as water) circulating through the hot water supply load 3 and a hot water supply refrigerant circulating through the hot water supply refrigeration cycle 2. . That is, the hot water supply refrigeration cycle 2 and the hot water supply load 3 are cascade-connected by the heat medium-refrigerant heat exchanger 51.
  • the hot water supply throttling means 22 functions as a pressure reducing valve and an expansion valve, and decompresses the hot water supply refrigerant to expand it.
  • the hot water supply throttling means 22 may be constituted by a controllable opening degree, such as a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary.
  • the refrigerant-refrigerant heat exchanger 41 performs heat exchange between the hot water supply refrigerant circulating in the hot water supply refrigeration cycle 2 and the air conditioning refrigerant circulating in the air conditioning refrigeration cycle 1.
  • the type of refrigerant circulating in the hot water supply refrigeration cycle 2 is not particularly limited.
  • natural refrigerants such as carbon dioxide, hydrocarbons and helium, alternative refrigerants not containing chlorine such as HFC410A, HFC407C, and HFC404A, or existing Any of chlorofluorocarbon refrigerants such as R22 and R134a used in this product may be used.
  • the hot water supply refrigerant that has been heated to a high temperature and high pressure by the hot water supply compressor 21 is discharged from the hot water supply compressor 21 and flows into the heat medium-refrigerant heat exchanger 51.
  • the flowing hot water supply refrigerant radiates heat by heating the water circulating in the hot water supply load 3.
  • This hot water supply refrigerant is expanded by the hot water supply throttling means 22 to a temperature equal to or lower than the outlet temperature of the refrigerant-refrigerant heat exchanger 41 in the hot water supply heat source circuit D of the air conditioning refrigeration cycle 1.
  • the expanded hot water supply refrigerant receives and evaporates from the air conditioning refrigerant flowing through the hot water supply heat source circuit D constituting the air conditioning refrigeration cycle 1 in the refrigerant-refrigerant heat exchanger 41, and returns to the hot water supply compressor 21.
  • the hot water supply load 3 includes a water circulation pump 31, a heat medium-refrigerant heat exchanger 51, and a hot water storage tank 32. That is, in the hot water supply load 3, the water circulation pump 31, the heat medium-refrigerant heat exchanger 51, and the hot water storage tank 32 are connected in series by the hot water storage water circulation pipe 203 to form a water circuit (heat medium circuit). This is achieved by circulating hot water supply water in this water circuit.
  • the operation of the hot water supply load 3 does not differ depending on the operating state of the air conditioning refrigeration cycle 1, that is, whether the cooling main operation is executed or the heating main operation is executed.
  • the hot water circulating pipe 203 constituting the water circuit is constituted by a copper pipe, a stainless pipe, a steel pipe, a vinyl chloride pipe, or the like.
  • the water circulation pump 31 sucks the water stored in the hot water storage tank 32, pressurizes the water, and circulates the inside of the hot water supply load 3.
  • the water circulation pump 31 is of a type whose rotational speed is controlled by an inverter. Configure.
  • the heat medium-refrigerant heat exchanger 51 exchanges heat between the heat medium (fluid such as water) circulating through the hot water supply load 3 and the hot water supply refrigerant circulating through the hot water supply refrigeration cycle 2. Is to do.
  • the hot water storage tank 32 stores water heated by the heat medium-refrigerant heat exchanger 51.
  • the relatively low temperature water stored in the hot water storage tank 32 is drawn from the bottom of the hot water storage tank 32 and pressurized by the water circulation pump 31.
  • the water pressurized by the water circulation pump 31 flows into the heat medium-refrigerant heat exchanger 51, and receives heat from the hot water supply refrigerant circulating in the hot water supply refrigeration cycle 2 by the heat medium-refrigerant heat exchanger 51. . That is, the water flowing into the heat medium-refrigerant heat exchanger 51 is boiled by the hot water supply refrigerant circulating in the hot water supply refrigeration cycle 2, and the temperature rises. Then, the boiled water returns to the relatively hot upper portion of the hot water storage tank 32 and is stored in the hot water storage tank 32.
  • the air conditioning refrigeration cycle 1 and the hot water supply refrigeration cycle 2 are independent refrigerant circuit configurations (the first refrigerant circuit constituting the air conditioning refrigeration cycle 1 and the hot water supply refrigeration cycle 2 constituting the first refrigerant circuit 1).
  • the refrigerant circulating through each refrigerant circuit may be the same type or different types. That is, the refrigerant in each refrigerant circuit flows so as to exchange heat with each other in the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 without being mixed.
  • a refrigerant having a low critical temperature when used as the hot water supply refrigerant, it is assumed that the hot water supply refrigerant in the heat dissipation process in the heat medium-refrigerant heat exchanger 51 enters a supercritical state when hot water supply is performed. .
  • the COP fluctuates greatly due to changes in the radiator pressure and the outlet temperature of the radiator, and more advanced control is required in order to obtain a high COP.
  • a refrigerant having a low critical temperature has a high saturation pressure for the same temperature, and accordingly, it is necessary to increase the thickness of the piping and the compressor, which causes an increase in cost.
  • the target temperature of hot water supply is often 60 ° C. or higher at a minimum. Is done.
  • a refrigerant having a critical temperature of 60 ° C. or higher is adopted as the hot water supply refrigerant. This is because, if such a refrigerant is employed as the hot water supply refrigerant of the hot water supply refrigeration cycle 2, a high COP can be obtained more stably at a lower cost.
  • the refrigerant is regularly used in the vicinity of the critical temperature, it is assumed that the refrigerant circuit has a high temperature and a high pressure. Therefore, the hot water supply compressor 21 is stabilized by using a compressor of a type using a high pressure shell. Driving is possible.
  • FIG. 1 shows an example in which two or more cooling indoor units B and heating indoor units C are connected, but the number of connected units is not particularly limited. It is only necessary that there is no heating indoor unit C or at least one unit is connected. And the capacity
  • the hot water supply load system is configured in a two-way cycle, and therefore when supplying high-temperature hot water supply demand (for example, 80 ° C.), What is necessary is just to make the temperature of the heat radiator of the refrigerating cycle 2 high temperature (for example, condensing temperature 85 degreeC), and when there is another heating load, it does not increase even to the condensing temperature (for example, 50 degreeC) of the heating indoor unit C. Energy saving. Also, for example, when there was a demand for hot water supply during the air conditioning and cooling operation in summer, it was necessary to provide it with a boiler, etc., but it was necessary to collect hot water that had been discharged into the atmosphere and reuse it. Therefore, the system COP is greatly improved and energy is saved.
  • high-temperature hot water supply demand for example, 80 ° C.
  • FIG. 2 is a schematic circuit configuration diagram for explaining another example of a hot water supply load (hereinafter referred to as a hot water supply load 3a).
  • a hot water supply load 3a An example of a mechanism for heating the water circulating in the hot water supply load 3a will be described with reference to FIG.
  • a hot water supply water circulation cycle (hot water supply heat medium circulation cycle) 4 includes a heat medium-refrigerant heat exchanger 51 and water-water heat. Cascade connection is performed via an exchanger (heat medium-heat medium heat exchanger) 201.
  • FIG. 1 is a schematic circuit configuration diagram for explaining another example of a hot water supply load (hereinafter referred to as a hot water supply load 3a).
  • An example of a mechanism for heating the water circulating in the hot water supply load 3a will be described with reference to FIG.
  • a hot water supply water circulation cycle (hot water supply heat medium circulation cycle) 4 includes a heat medium-refrigerant heat exchanger 51 and water-water heat. Ca
  • FIG. 1 shows an example in which water is directly heated (heated up) by a heat medium-refrigerant heat exchanger 51 in an open circuit hot water supply load 3, but FIG. 2 shows hot water supply water.
  • An example is shown in which a circulation cycle 4 is provided and water is indirectly heated by the water-water heat exchanger 201 in the open circuit hot water supply load 3a.
  • the hot water supply water circulation cycle 4 includes a heat medium circulation pump 31 a, a heat medium-refrigerant heat exchanger 51, and a water-water heat exchanger 201.
  • the hot water supply water circulation cycle 4 includes a heat circuit circulation pump 31a, a heat medium-refrigerant heat exchanger 51, and a water-water heat exchanger 201 connected in series by a circulation water pipe 202 to form a water circuit (heat This is established by configuring a medium circuit) and circulating a heating heat medium (heating water) through the heat medium circuit (water circuit).
  • the circulating water pipe 202 constituting the water circuit is constituted by a copper pipe, a stainless pipe, a steel pipe, a vinyl chloride pipe, or the like.
  • the heat medium circulation pump 31a sucks water (heat medium) that is conducted through the circulation water pipe 202, pressurizes the water, and circulates the hot water supply water circulation cycle 4.
  • the rotation speed is increased by an inverter. It is good to comprise by the type by which is controlled.
  • the heat medium-refrigerant heat exchanger 51 performs heat exchange between the water circulating in the hot water supply water circulation cycle 4 and the hot water supply refrigerant circulating in the hot water supply refrigeration cycle 2.
  • the water-water heat exchanger 201 performs heat exchange between the water circulating through the hot water supply water circulation cycle 4 and the water circulating through the hot water supply load 3a.
  • other fluids such as brine (antifreeze) may be circulated as a heat medium.
  • the relatively low temperature water stored in the hot water storage tank 32 is drawn from the bottom of the hot water storage tank 32 and pressurized by the water circulation pump 31.
  • the water pressurized by the water circulation pump 31 flows into the water-water heat exchanger 201, and receives heat from the water circulating in the hot water supply water circulation cycle 4 by the water-water heat exchanger 201. That is, the water flowing into the water-water heat exchanger 201 is boiled by the water circulating in the hot water supply water circulation cycle 4 and the temperature rises. Then, the boiled water returns to the relatively hot upper portion of the hot water storage tank 32 and is stored in the hot water storage tank 32. That is, heat from the hot water supply refrigeration cycle 2 is transmitted to the hot water supply water circulation cycle 4 by the heat medium-refrigerant heat exchanger 51 and to the hot water supply load 3a by the water-water heat exchanger 201, respectively. .
  • FIG. 3 is an explanatory diagram for explaining an example of the structure of the outdoor heat exchanger 103. Based on FIG. 3, the outdoor heat exchanger 103 which enabled the heating operation through the year is demonstrated.
  • the air conditioning and hot water supply complex system 100 is used only for normal air conditioning applications, it is common to perform the heating operation at an outdoor air wet bulb temperature of 15 ° C. or less. However, when performing the hot water supply operation, the hot water supply operation is performed regardless of the outside air temperature. Need to do. Therefore, FIG. 3 shows an example in which the outdoor heat exchanger 103 has a divided structure having a plurality of heat exchangers (hereinafter referred to as a divided heat exchanger 103a).
  • the outdoor heat exchanger 103 may have a divided structure in which four heat exchangers are combined, or may have a divided structure in which one heat exchanger is divided into four.
  • the high-pressure side connection pipe 106 is branched into a plurality of parts and connected to each of the divided heat exchangers 103 a constituting the outdoor heat exchanger 103.
  • each of the branched high-pressure side connection pipes 106 is provided with an electromagnetic valve 209 that is an on-off valve that is controlled to be opened and closed so as not to conduct the refrigerant.
  • one of the high-pressure side connection pipes 106 branched into a plurality is a bypass circuit 300 that bypasses the divided heat exchanger 103a.
  • the bypass circuit 300 is also provided with a solenoid valve 209a that is a bypass on-off valve.
  • the outdoor heat exchanger 103 constituting the air-conditioning refrigeration cycle 1 can adjust the amount of refrigerant flowing in by controlling the opening and closing of the solenoid valve 209 and the solenoid valve 209a, and the heat exchanger capacity can be divided. It has become.
  • the heat exchanger capacity of the outdoor heat exchanger 103 is reduced. It is desirable to make it. Therefore, in the air conditioning and hot water supply complex system 100, all or part of the solenoid valve 209 is controlled to be closed so that the refrigerant flowing into the outdoor heat exchanger 103 is shut off so as not to deviate from the operating range of the air conditioning compressor 101. .
  • the number of divided heat exchangers 103a into which refrigerant flows is determined in accordance with the operating range of the air conditioning compressor 101, and the inflow amount of refrigerant is adjusted by closing control of the electromagnetic valve 209 according to the number.
  • the operation range of the air conditioning compressor 101 is not deviated.
  • the operation range of the air conditioning compressor 101 may be deviated.
  • the solenoid valve 209 a installed in the bypass circuit 300 is controlled to be opened so that the refrigerant is returned to the suction side of the air-conditioning compressor 101 without flowing into the outdoor heat exchanger 103.
  • the solenoid valve 209a installed in the bypass circuit 300 has an equation Cva ⁇ if the flow coefficient of refrigerant flowing through the bypass circuit 300 is CVb, where Cva is the flow coefficient of refrigerant when passing through the outdoor heat exchanger 103. It is selected so as to satisfy CVb. Furthermore, when the operation range of the air conditioning compressor 101 cannot be maintained only by dividing the heat exchanger capacity, the operation range is maintained by opening the electromagnetic valve 209a installed in the bypass circuit 300 to bypass the refrigerant. Note that the split structure may be controlled using an electronic expansion valve instead of using an electromagnetic valve.
  • FIG. 4 is a schematic circuit configuration diagram for explaining still another example of the hot water supply load (hereinafter referred to as a hot water supply load 3b).
  • FIG. 5 is a schematic circuit diagram showing an example of circulation of the heat medium (fluid such as water serving as a heat source) in the hot water supply load 3b.
  • FIG. 6 is a flowchart showing a heat medium flow path switching process in the hot water supply load 3b. An example of a mechanism for heating the heat medium circulating in the hot water supply load 3b (that is, the heat medium circulating in the water circuit of the hot water supply load 3b) will be described with reference to FIGS.
  • two flow paths (flow path A and flow path B) are shown together.
  • the flow path A represents the flow path for circulating the heat medium via the bypass pipe 303
  • the flow path B represents the flow path for circulating the heat medium without passing the bypass pipe 303, respectively.
  • the hot water supply load 3b is provided with a first flow path switching device 301 in a hot water storage water circulation pipe 203 between the hot water storage tank 32 and the water circulation pump 31, and a heat medium-refrigerant heat exchanger 51 and
  • a second flow path switching device 302 is provided in the hot water circulation pipe 203 between the hot water storage tank 32, and the first flow path switching device 301 and the second flow path switching device 302 are connected by a bypass pipe 303 via an auxiliary tank 305. It is configured by connecting.
  • the hot water storage water circulation pipe 203 is connected in series, the bypass circuit 303 is provided in the water circuit (heat medium circuit), and the hot water supply water can be circulated through the bypass pipe 303.
  • the hot water supply load 3b is provided with a first temperature sensor 310 and a second temperature sensor 311.
  • the auxiliary tank 305 stores water heated by the heat medium-refrigerant heat exchanger 51, similarly to the hot water storage tank 32.
  • the first flow path switching device 301 and the second flow path switching device 302 switch the water flow path to either the hot water storage water circulation pipe 203 or the bypass pipe 303, and are composed of, for example, a mixing valve or a three-way valve. ing.
  • the mixing valve is controlled to be opened and closed so that the ratio of circulating the low-temperature heat medium circulating in the water circuit and the ratio of circulating the high-temperature heat medium can be adjusted.
  • a predetermined tapping temperature can be maintained by controlling the ratio of the open / close area (flow channel cross-sectional area) of the mixing valve.
  • the three-way valve switches the flow path of the heat medium (the flow path via the bypass pipe 303 or the flow path not via the bypass pipe 303). *
  • the first temperature sensor 310 is provided on the upstream side of the first flow path switching device 301, that is, on the inlet side of the heat medium-refrigerant heat exchanger 51, and determines the inlet temperature of the heat medium temperature circulated to the hot water supply load 3b.
  • a thermistor is used.
  • the second temperature sensor 311 is provided on the upstream side of the second flow path switching device 302, that is, on the outlet side of the heat medium-refrigerant heat exchanger 51, and the outlet temperature of the heat medium temperature circulated to the hot water supply load 3b.
  • a thermistor is used.
  • the hot water supply compressor 21 When supplying a heat medium to the hot water supply load 3b side in the water circuit of the hot water supply load 3b, the hot water supply compressor 21 is started to send the heat medium, and the hot water supply refrigeration cycle 2 starts operation.
  • the hot water supply refrigeration cycle 2 When the hot water supply refrigeration cycle 2 is activated, the first flow sensor 301 and the first flow switching device 301 and the second flow sensor 311 are measured while the heat medium temperature circulated on the hot water supply load 3 b side is measured by the first temperature sensor 310 and the second temperature sensor 311. After passing through the two-channel switching device 302 and exchanging heat with the heat medium-refrigerant heat exchanger 51, it is sent to the hot water supply load side (hot water storage tank 32 side).
  • the first temperature sensor 310 measures the heat medium temperature, and the first flow path switching device 301 and the first flow switching device 301.
  • the flow path of water can be switched by the two-flow path switching device 302, that is, the heat medium can be circulated through the bypass pipe 303.
  • the temperature of the small-capacity heat medium can be raised, and the low-efficiency operation time at the time of startup can be shortened. Therefore, the operating efficiency is improved by increasing the start-up time of the hot water supply refrigeration cycle 2 at the start-up.
  • a high-temperature heat medium can be always supplied by heating a small capacity heat medium.
  • step S101 when the hot water supply compressor 21 is activated, the heat medium temperature is measured by the first temperature sensor 310 and the second temperature sensor 311 (step S101). Then, the inlet temperature measured by the first temperature sensor 310 is compared with a predetermined determination temperature A ° C. (step S102). When the inlet temperature is higher than A ° C. (inlet temperature> A ° C.) (step S102; YES), the water circuit of the hot water supply load 3b is changed to the flow path B (step S103). That is, a high-temperature heat medium is supplied through the flow path B not passing through the bypass pipe 303, and the boiling operation is performed.
  • step S104 the water circuit of the hot water supply load 3b is changed to the flow path A (step S104). That is, the heat medium is circulated until the condition of the inlet temperature> A ° C. is satisfied by boiling a small-capacity heat medium in the flow path A through the bypass pipe 303.
  • the flow path is switched using the heat medium temperature as the determination threshold. Also good.
  • the determination temperature A is determined by the operating range of the hot water supply compressor 21 used in the hot water supply refrigeration cycle 2, and is set to a temperature equal to or higher than the temperature obtained by converting the lowest low pressure to the saturated temperature.
  • 4 to 6 show an example in which the first flow path switching device 301 and the second flow path switching device 302 are configured by a single valve, but the configuration may be configured by using a plurality of valves. May be. Furthermore, the first flow path switching device 301 and the second flow path switching device 302 may be configured using, for example, an electronic expansion valve or a plurality of electromagnetic valves.
  • the configuration in which the auxiliary tank 305 is provided in the hot water supply load 3b is shown as an example, the configuration is not limited thereto, and the configuration may be such that the auxiliary tank 305 is not provided and only the bypass pipe 303 is provided. In this case, paying attention to the capacity in the bypass pipe 303, the pipe length and the pipe inner diameter of the bypass pipe 303 may be determined. Further, the capacity of the auxiliary tank 305 is not particularly limited.
  • the auxiliary tank 305 may have a capacity that can store a small-capacity heat medium. The capacity of the heat medium will be described in detail with reference to FIG.
  • Control of each device of the air conditioning and hot water supply complex system 100 is executed by a control device (not shown) configured by a microcomputer or the like.
  • This control device may be provided in any of the heat source unit A or the relay unit E, the cooling indoor unit B, the heating indoor unit C, and the hot water supply heat source circuit D. Temperature information measured by the first temperature sensor 310 and the second temperature sensor 311 is transmitted to the control device.
  • Low pressure detection means such as a pressure sensor for detecting the pressure of refrigerant sucked into the air conditioning compressor 101 is provided in the suction side pipe connected to the air conditioning compressor 101, and pressure information measured by the pressure sensor is provided. May be transmitted to the control device.
  • the number of the divided heat exchangers 103a constituting the outdoor heat exchanger 103 that is, the number of divided heat exchangers 103 is not particularly limited.
  • FIG. 7 is a graph showing an example of the operating range of the hot water supply compressor 21. Based on FIG. 7, an example of the operating range of the hot water supply compressor 21 mounted in the air conditioning refrigeration cycle 1 will be described.
  • the horizontal axis represents Ps (suction pressure) of the hot water supply compressor 21, and the vertical axis represents Pd (discharge pressure) of the hot water supply compressor 21.
  • the operating range of the hot water supply compressor 21 shown in FIG. 7 shows a case where R134a is used as the refrigerant circulating in the hot water supply refrigeration cycle 2.
  • (1) to (3) shown in the figure indicate temperature zones when heating the heat source load.
  • (1) shows the use area at the time of initial startup of the hot water supply compressor 21.
  • the use area of the hot water supply compressor 21 at this time is generally a heat medium temperature of 5 ° C. to 25 ° C. when the heat medium temperature is in the minimum use temperature range.
  • (2) shows a usage region when the hot water supply compressor 21 is driven while limiting the maximum frequency so as not to leave the initial starting state and deviate from the compressor operating range.
  • the use area of the hot water supply compressor 21 at this time is generally a heat medium temperature of 25 ° C. to 45 ° C.
  • (3) shows a use area when the hot water supply compressor 21 overheats to a necessary temperature area as a hot water supply application.
  • the use area of the hot water supply compressor 21 at this time is generally a heat medium temperature of 45 ° C. to 90 ° C. From FIG. 7, it can be seen that R134a can be used for hot water supply and heating applications.
  • FIG. 8 is a graph showing another example of the operating range of the hot water supply compressor 21. Based on FIG. 8, another example of the operating range of the hot water supply compressor 21 mounted in the air conditioning refrigeration cycle 1 will be described.
  • the horizontal axis represents Ps (suction pressure) of the hot water supply compressor 21, and the vertical axis represents Pd (discharge pressure) of the hot water supply compressor 21.
  • the operating range of the hot water supply compressor 21 shown in FIG. 8 shows a case where R410A is used as the refrigerant circulating in the hot water supply refrigeration cycle 2.
  • (1) to (3) shown in the figure indicate temperature zones when heating the heat source load.
  • (1) shows the use area at the time of initial startup of the hot water supply compressor 21.
  • the use area of the hot water supply compressor 21 at this time is generally a heat medium temperature of 5 ° C. to 15 ° C. when the heat medium temperature is in the minimum use temperature range.
  • (2) shows a usage region when the hot water supply compressor 21 is driven while limiting the maximum frequency so as not to leave the initial starting state and deviate from the compressor operating range.
  • the use area of the hot water supply compressor 21 at this time is generally a heat medium temperature of 15 ° C. to 45 ° C.
  • (3) shows a use area when the hot water supply compressor 21 overheats to a necessary temperature area as a hot water supply application.
  • the use area of the hot water supply compressor 21 at this time is generally a heat medium temperature of 45 ° C. to 68 ° C.
  • R410A can be used as a hot water supply application and a heating application.
  • the critical temperature of the refrigerant is 68.3 ° C.
  • R410A is used for heating (generally 45 ° C.)
  • R134a and R410A are suitable as the refrigerant circulating in the hot water supply refrigeration cycle 2.
  • 7 and 8 show the operation range of the hot water supply compressor 21 when R134a or R410A is used.
  • a refrigerant with a critical temperature of 70 ° C. or higher for hot water use, and for a refrigerant with a temperature of 70 ° C. or lower, heating is performed. High-efficiency operation is possible by using it as an application.
  • FIG. 9 is a graph showing the opening / closing area ratio of the first flow path switching device 301. Based on FIG. 9, the ratio of the open / close area when the first flow path switching device 301 is configured by a mixing valve will be described. 4 to 6, assuming that the first flow path switching device 301 is a three-way valve, the case where the heat medium (fluid such as water) is boiled by switching the flow path to either one has been described. In FIG. 9, assuming that the first flow path switching device 301 is a mixing valve, a case where the heat medium is boiled while mixing the high-temperature heat medium and the low-temperature heat medium will be described. In FIG. 9, the horizontal axis represents pulse, and the vertical axis represents the open / close area ratio. Further, the line (A) represents the flow path A, and the line (B) represents the flow path B.
  • the mixing valve is usually configured to realize output at a target temperature by changing the opening area of the flow path when mixing a high-temperature heat medium and a low-temperature heat medium.
  • the first flow path switching device 301 is started from [START] shown in FIG.
  • the flow path A is 70 ° C. (line (A))
  • the flow path B is 10 ° C. (line (B))
  • the target temperature is 40 ° C. From the opening area ratio, the opening degree (opening area) is 0.5, and the target temperature is output.
  • the mixing valve By applying a mixing valve having characteristics as shown in FIG. 9 to the first flow path switching device 301, a constant tapping temperature can always be output. That is, by applying the mixing valve to the first flow path switching device 301, even when a sudden transient change occurs, it is possible to cope with it by changing the opening area ratio according to the transient change. Therefore, compared with the case where the three-way valve for switching the flow path to either one is applied to the first flow path switching device 301, an operation with further improved efficiency can be realized.
  • the first flow path switching device 301 is described as an example, but it goes without saying that the same applies to the second flow path switching device 302.
  • FIG. 10 is a graph showing a case where the opening / closing area ratio of the first flow path switching device 301 is shifted. Based on FIG. 10, the case where the ratio of the opening and closing area in the case where the 1st flow-path switching apparatus 301 is comprised with a mixing valve is shifted is demonstrated.
  • FIG. 9 illustrates an example in which the open / close area ratio of the first flow path switching device 301 is not shifted.
  • FIG. 10 illustrates an example in which the open / close area ratio of the first flow path switching device 301 is shifted. To do.
  • the horizontal axis represents pulse and the vertical axis represents the open / close area ratio.
  • the line (A) represents the flow path A
  • the line (B) represents the flow path B.
  • the operation to the set temperature is low in applications where the high temperature heat medium is often used. Therefore, by shifting the opening area ratio of the first flow path switching device 301, the target temperature can be reached earlier than the opening area ratio shown in FIG.
  • the flow path A and the flow path B are shown as straight lines having no inflection point, but a mixing valve having a characteristic having an inflection point is applied to the first flow path switching device 301. Also good.
  • the first flow path switching device 301 is described as an example, but it goes without saying that the same applies to the second flow path switching device 302.
  • FIG. 11 is a graph showing the relationship between the volume of the auxiliary tank 305 and the volume of the heat medium-refrigerant heat exchanger 51. Based on FIG. 11, the capacity of the heat medium to be conducted to the bypass pipe 303 will be described from the relationship between the volume of the auxiliary tank 305 and the volume of the heat medium-refrigerant heat exchanger 51.
  • the horizontal axis represents the volume of the auxiliary tank 305
  • the vertical axis represents the volume of the heat medium-refrigerant heat exchanger 51.
  • the line (A) shows the case where the volume of the auxiliary tank 305 and the volume of the heat medium-refrigerant heat exchanger 51 are the same, and the line (B) shows the volume of the auxiliary tank 305 is the volume of the heat medium-refrigerant heat exchanger 51.
  • the line (C) represents the case where the volume of the auxiliary tank 305 is larger than the volume of the heat medium-refrigerant heat exchanger 51, respectively.
  • the boiling operation is performed at the minimum capacity, and the minimum capacity is heated up. It can be boiled in the shortest time.
  • the volume of the auxiliary tank 305 is smaller than the volume of the heat medium-refrigerant heat exchanger 51 (line (B))
  • the minimum required amount is insufficient, so the capacity required for the initial boiling is insufficient, and the hot water temperature is insufficient. End up.
  • the volume of the auxiliary tank 305 is larger than the volume of the heat medium-refrigerant heat exchanger 51 (line (C))
  • the initial boiling is performed more than necessary, so that it takes time until the unit starts up and energy saving operation is not performed.
  • the tank capacity that can be operated with the highest efficiency is the same as the amount (volume) of water retained in the heat medium-refrigerant heat exchanger 51. Therefore, the volume of the auxiliary tank 305 may be determined from the volume of the heat medium-refrigerant heat exchanger 51.
  • a heat medium having the same capacity as the amount of water held in the heat medium-refrigerant heat exchanger 51 can be conducted to the bypass pipe 303 without the auxiliary tank 305. If it is possible, a highly efficient operation can be realized.

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Abstract

L'invention concerne un système complexe de climatisation et d'alimentation en eau chaude, la charge de refroidissement, la charge de chauffage et la charge d'alimentation en eau chaude à température élevée pouvant être traitées de manière simultanée, une source de chaleur stabilisée pouvant être fournie toute l'année, la montée au moment du démarrage du système pouvant être accélérée. Le système composite (100) est caractérisé en ce qu'un tuyau de dérivation (303) à des fins de raccordement entre un échangeur de chaleur à fluide caloporteur/liquide de refroidissement (51) et un réservoir d'alimentation en eau chaude (32) et à des fins de raccordement entre le réservoir d'alimentation en eau chaude (32) et une pompe de circulation d'eau (31) est mis en œuvre dans le circuit d'eau de la charge d'alimentation en eau chaude (3b).
PCT/JP2009/050407 2009-01-15 2009-01-15 Système complexe de climatisation et d'alimentation en eau chaude Ceased WO2010082324A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP09838294.8A EP2378223B1 (fr) 2009-01-15 2009-01-15 Système complexe de climatisation et d'alimentation en eau chaude
PCT/JP2009/050407 WO2010082324A1 (fr) 2009-01-15 2009-01-15 Système complexe de climatisation et d'alimentation en eau chaude
JP2010546506A JP5264936B2 (ja) 2009-01-15 2009-01-15 空調給湯複合システム

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/050407 WO2010082324A1 (fr) 2009-01-15 2009-01-15 Système complexe de climatisation et d'alimentation en eau chaude

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GB2486646A (en) * 2010-12-20 2012-06-27 Sublogic Mfg Ltd Method and Apparatus for Cascade Refrigeration and for Central Heating Hot Water Supply
WO2012114462A1 (fr) * 2011-02-22 2012-08-30 株式会社日立製作所 Système de conditionnement d'air/d'alimentation en eau chaude et procédé de commande d'un tel système
JP2012220145A (ja) * 2011-04-12 2012-11-12 Purpose Co Ltd 蓄熱装置およびその凍結予防方法
EP2423612A3 (fr) * 2010-08-25 2015-08-05 Hitachi Appliances, Inc. Système de climatisation
EP3561396A1 (fr) * 2010-11-05 2019-10-30 LG Electronics Inc. Appareil d'alimentation en eau chaude pour utilisation combinée de climatiseur
CN110553419A (zh) * 2019-09-30 2019-12-10 天津商业大学 一种家庭能源智能时空输配系统

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WO2013161011A1 (fr) * 2012-04-25 2013-10-31 株式会社日立製作所 Système de conditionnement d'air/d'alimentation en eau chaude
KR20250015212A (ko) * 2023-07-24 2025-02-03 엘지전자 주식회사 열공급장치

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CN101929445A (zh) * 2010-08-13 2010-12-29 东华大学 一种分布式太阳能热/冷-电联供系统
EP2423612A3 (fr) * 2010-08-25 2015-08-05 Hitachi Appliances, Inc. Système de climatisation
EP3561396A1 (fr) * 2010-11-05 2019-10-30 LG Electronics Inc. Appareil d'alimentation en eau chaude pour utilisation combinée de climatiseur
GB2486646A (en) * 2010-12-20 2012-06-27 Sublogic Mfg Ltd Method and Apparatus for Cascade Refrigeration and for Central Heating Hot Water Supply
WO2012114462A1 (fr) * 2011-02-22 2012-08-30 株式会社日立製作所 Système de conditionnement d'air/d'alimentation en eau chaude et procédé de commande d'un tel système
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JP2012220145A (ja) * 2011-04-12 2012-11-12 Purpose Co Ltd 蓄熱装置およびその凍結予防方法
CN110553419A (zh) * 2019-09-30 2019-12-10 天津商业大学 一种家庭能源智能时空输配系统

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EP2378223B1 (fr) 2019-04-24
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JPWO2010082324A1 (ja) 2012-06-28
EP2378223A1 (fr) 2011-10-19

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