WO2011061792A1 - 冷凍サイクル装置及びそれに適用される情報伝達方法 - Google Patents

冷凍サイクル装置及びそれに適用される情報伝達方法 Download PDF

Info

Publication number
WO2011061792A1
WO2011061792A1 PCT/JP2009/006177 JP2009006177W WO2011061792A1 WO 2011061792 A1 WO2011061792 A1 WO 2011061792A1 JP 2009006177 W JP2009006177 W JP 2009006177W WO 2011061792 A1 WO2011061792 A1 WO 2011061792A1
Authority
WO
WIPO (PCT)
Prior art keywords
hot water
water supply
refrigerant
unit
refrigeration cycle
Prior art date
Application number
PCT/JP2009/006177
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
松井賢治
▲高▼田茂生
薮内宏典
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP09851418.5A priority Critical patent/EP2503266B1/de
Priority to JP2011541733A priority patent/JP5642085B2/ja
Priority to PCT/JP2009/006177 priority patent/WO2011061792A1/ja
Priority to CN200980162495.5A priority patent/CN102695929B/zh
Priority to US13/510,150 priority patent/US20120222440A1/en
Publication of WO2011061792A1 publication Critical patent/WO2011061792A1/ja

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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 applied to an air conditioning apparatus or an air conditioning and hot water supply complex system and an information transmission method applied thereto, and relates to a refrigeration cycle apparatus designed to improve the system COP and an information transmission method applied thereto. Is.
  • an air conditioning and hot water supply complex system that can simultaneously supply a cooling load, a heating load, and a hot water supply load, including an air conditioning and hot water supply complex system as described in Patent Document 1, the cooling load, the heating load, and the hot water supply load are balanced. It has been conventionally known that the system COP is improved. However, in reality, the air conditioning load and hot water supply load required by the user have different time zones and required amounts, so that efficient operation with improved system COP has not necessarily been realized. . For example, in summer, the cooling load increases mainly during the daytime, and the hot water supply load increases during the night when many baths and showers are used, and the operating time corresponds to the air conditioning load and hot water load. Usually the bands are different.
  • the motor efficiency of the compressor operated at a low speed by the inverter is deteriorated at the time of small capacity operation, so that the energy consumption efficiency is deteriorated.
  • the operation condition is a heating overload and small capacity operation, the high pressure becomes too high, and the situation that the operation cannot be continued occurs. There was also.
  • the present invention has been made in order to solve the above-described problems, and is intended to balance the load balance (for example, the balance between the cooling load and the heating load, and the balance between the cooling load and the heating load and the hot water supply load).
  • An object of the present invention is to provide an improved refrigeration cycle apparatus and an information transmission method applied thereto.
  • the refrigeration cycle apparatus includes at least one heat source unit on which at least an air conditioning compressor and a heat source side heat exchanger are mounted, a plurality of usage side units on which at least a usage side heat exchanger is mounted, A refrigeration cycle apparatus comprising a heat source unit and the use side unit, and comprising at least one relay unit that transmits the heat or cold generated by the heat source side unit to the use side unit; The plurality of usage-side units are operated so as to balance the cooling load and the heating load executed by the plurality of usage-side units.
  • An information transmission method is an information transmission method applied to the above-described refrigeration cycle apparatus, wherein the heat source unit has a heat source unit controller, the relay unit has a relay unit controller, and the user side unit has an information transmission method.
  • the heat source unit has a heat source unit controller
  • the relay unit has a relay unit controller
  • the user side unit has an information transmission method.
  • Each is provided with a usage-side unit controller, and the load balance of the plurality of usage-side units can be determined by one of the controllers by transmitting information from each controller.
  • the plurality of usage-side units are operated so as to balance the cooling load and the heating load executed by the plurality of usage-side units, thereby improving the system COP and saving energy. It is possible to reduce the running cost while realizing it.
  • the information transmission method according to the present invention is applied to the above-described refrigeration cycle apparatus, so that stable operation can be continued efficiently.
  • FIG. 1 is a refrigerant circuit diagram illustrating an example of a 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 based on FIG.
  • the refrigeration cycle apparatus 100 uses a refrigeration cycle that circulates refrigerant (air conditioning refrigerant) to simultaneously supply a cooling load (cooling load), a heating load, and a hot water supply load (heating load).
  • the case is shown as an example.
  • the relationship of the size of each component may be different from the actual one.
  • the refrigeration cycle apparatus 100 includes an air conditioning refrigeration cycle 1, a hot water supply refrigeration cycle 2, and a hot water supply load 3.
  • the air conditioning refrigeration cycle 1 and the hot water supply refrigeration cycle 2 are refrigerant-refrigerant heat exchangers. 41, the hot water supply refrigeration cycle 2 and the hot water supply load 3 are configured to perform heat exchange in a heat medium-refrigerant heat exchanger 51 without mixing the refrigerant and water.
  • the refrigeration cycle apparatus 100 is equipped with a hot water supply unit F.
  • the air-conditioning refrigeration cycle 1 includes a heat source unit A, an indoor unit B in charge of a cooling load or a heating load, an indoor unit C, a hot water supply heat source circuit D serving as a heat source for the hot water supply refrigeration cycle 2, and a relay unit E. It is constituted by. Among these, the indoor unit B, the indoor unit C, and the hot water supply heat source circuit D are connected and mounted in parallel to the heat source unit A. And the relay unit E installed between the heat source unit A, the indoor unit B, the indoor unit C, and the hot water supply heat source circuit D switches the flow of the refrigerant, so that the indoor unit B, the indoor unit C, and the hot water supply heat source are switched. Each function as the circuit D is exhibited.
  • the heat source unit A has a function of supplying hot or cold to the indoor unit B, the indoor unit C, and the hot water supply heat source circuit D.
  • an air conditioning compressor 101 a four-way valve 102, an outdoor heat exchanger (heat source side heat exchanger) 103, and an accumulator 104 are connected in series.
  • 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 and a radiator (condenser), exchanges heat between air supplied from a blower (not shown) and the air-conditioning refrigerant, and converts the air-conditioning refrigerant into an evaporative gas. Or it is condensed and liquefied.
  • the accumulator 104 is disposed on the suction side of the air conditioning compressor 101, and stores excess air conditioning refrigerant.
  • the accumulator 104 may be any container that can store excess air-conditioning refrigerant.
  • the heat source unit A is supplied with a flow of air-conditioning refrigerant only in a predetermined direction (direction from the heat source unit A to the relay unit E) through the high-pressure side connection pipe 106 between the outdoor heat exchanger 103 and the relay unit E. Allow the flow of air-conditioning refrigerant only in a predetermined direction (direction from the relay unit E to the heat source unit A) to the check valve 105a and the low-pressure side connection pipe 107 between the four-way valve 102 and the relay unit E.
  • a check valve 105b is provided.
  • the high-pressure side connection pipe 106 and the low-pressure side connection pipe 107 are 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.
  • the second connection pipe 131 connecting the downstream side (connection portion b) of the check valve 105a and the downstream side (connection portion d) of the check valve 105b is connected.
  • 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 indoor unit B and the indoor unit C have a function of receiving heating or cooling supply from the heat source unit A and taking charge of heating load or cooling load.
  • an air conditioning throttle means 117 and an indoor heat exchanger (use side heat exchanger) 118 are connected in series and mounted. Further, the indoor unit B and the indoor unit C are illustrated as an example in which two air conditioning throttle means 117 and two indoor heat exchangers 118 are mounted in parallel.
  • the relay unit E determines, for example, that the indoor unit B is in charge of the cooling load and the indoor unit C is in charge of the heating load.
  • the connecting pipe connecting the relay unit E to the indoor heat exchanger 118 is called a connecting pipe 133
  • the connecting pipe connecting the relay unit E to the air conditioning throttle means 117 is called a connecting pipe 134.
  • 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) and an evaporator, and performs heat exchange between air supplied from a 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 has a function of supplying the hot or cold heat from the heat source unit A to the hot water supply refrigeration cycle 2 via the refrigerant-refrigerant heat exchanger 41.
  • the hot water supply heat source circuit D includes a hot water supply heat source throttle means 119 and a refrigerant-refrigerant heat exchanger 41 connected in series. That is, the air-conditioning refrigeration cycle 1 and the hot water supply refrigeration cycle 2 are cascade-connected via the refrigerant-refrigerant heat exchanger 41.
  • connection pipe connecting the relay unit E to the refrigerant-refrigerant heat exchanger 41 is connected to the connection pipe 135, and the connection pipe connecting the relay unit E to the hot water supply heat source throttle means 119 is the connection 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 connects the use side unit (the indoor unit B, the indoor unit C, and the hot water supply heat source circuit D) and the heat source unit A and either 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, or the refrigerant-refrigerant heat exchanger 41 is a chiller or a hot water heater.
  • This relay unit 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.
  • 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 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 unit 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 operation of the refrigeration cycle 1 for air conditioning will be described.
  • the operation when the indoor unit B is in charge of the cooling load, the indoor unit C is in charge of the heating load, and the hot water supply heat source circuit D is in charge of the hot water supply load will be described.
  • 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 unit 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 indoor unit C and the hot water supply heat source circuit D.
  • the air-conditioning refrigerant flowing into the indoor unit C dissipates heat in the indoor heat exchanger 118 (that is, warms the indoor 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, heat is supplied 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 unit C joins at the first meeting part 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 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 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 109b is Then, the low pressure side connecting pipe 107 joins.
  • the air-conditioning refrigerant that has passed through the second relay throttle unit 114 evaporates by exchanging heat in the second internal heat exchanger 113 and the first internal heat exchanger 111, and in the indoor unit in 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 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 via 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 heat 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 evaporates, 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 hot water circulation 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 a 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.
  • coolant was stored by the liquid receiver (accumulator 104) in the refrigerating cycle 1 for an air conditioning was shown, it is not restricted to this, It is stored with the heat exchanger used as a heat radiator in a refrigerating cycle. In this case, the accumulator 104 may be removed.
  • FIG. 1 the case where two or more indoor units B and C are connected is shown as an example, but the number of connected units is not particularly limited. For example, one or more indoor units B are It is sufficient that there is no indoor unit C or one or more indoor units C are 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 cycle 2 high (for example, condensing temperature 85 ° C.), and when there is another heating load, it is not necessary to increase even the condensing temperature (for example 50 ° C.) of indoor unit C. So it becomes 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.
  • Hot water supply unit F In the hot water supply unit F, a refrigerant-refrigerant heat exchanger 41, a hot water supply heat source throttle means 119, a heat medium-refrigerant heat exchanger 51, a hot water supply compressor 21, and a hot water supply throttle means 22 are mounted. ing.
  • the hot water supply unit F includes a part of the air-conditioning refrigeration cycle 1 through the refrigerant-refrigerant heat exchanger 41, a whole of the hot water supply refrigeration cycle 2, and a hot water supply through the heat medium-refrigerant heat exchanger 51. A part of the load 3 is accommodated.
  • FIG. 2 is a schematic configuration diagram for explaining information transmission in the refrigeration cycle apparatus 100 according to the embodiment of the present invention. Based on FIG.1 and FIG.2, the information transmission which the refrigeration cycle apparatus 100 performs is demonstrated.
  • two indoor units indoor unit B, indoor unit C
  • two hot water supply units F hot water supply unit F1, hot water supply unit F2
  • the refrigeration cycle apparatus 100 in a connected state is shown as an example.
  • the heat source unit A and the relay unit E are connected by the refrigerant pipe 5 (the high-pressure side connection pipe 106 and the low-pressure side connection pipe 107).
  • the side unit is connected by a refrigerant pipe 6 (connection pipe 133, connection pipe 134, connection pipe 135, connection pipe 136) and constitutes one refrigerant circuit system (air-conditioning refrigeration cycle 1).
  • the heat source unit A has a heat source unit controller 61
  • the relay unit E has a relay unit controller 62
  • the indoor units B and C have an indoor unit controller (use side unit controller) 63
  • the hot water supply unit F has A hot water supply unit controller (use side unit controller) 64 is provided.
  • the heat source unit A is the heat source unit controller 61
  • the relay unit E is the relay unit controller 62
  • the indoor unit B and the indoor unit C are the indoor unit controller 63
  • the hot water supply unit F is the hot water supply unit controller. 64. Each is controlled.
  • the heat source unit controller 61 and the relay unit controller 62 are connected via the transmission line 7 so as to be able to transmit information to each other.
  • the relay unit controller 62 and the indoor unit controller 63 are connected via the transmission line 8 so as to be able to transmit information to each other.
  • the relay unit controller 62 and the hot water supply unit controller 64 are connected via the transmission line 8 so as to be able to transmit information to each other.
  • the indoor unit controller 63 and the hot water supply unit controller 64 are connected to each other via a remote controller 65 and a transmission line 9 so as to be able to transmit information to each other.
  • heat source unit controller 61 is connected to a heat source unit controller (not shown) of another refrigerant system via the transmission line 10.
  • a centralized controller 66 for centrally managing the refrigeration cycle apparatus 100 is further connected to the transmission line 10.
  • the heat source unit controller 61, the relay unit controller 62, the indoor unit controller 63, the hot water supply unit controller 64, the remote controller 65, and the centralized controller 66 are each assigned a unique address, and when the system is started by manual setting processing or automatic discrimination processing It is designed to know the address of the communication partner. Further, the heat source unit controller 61 is configured to grasp the driving capabilities of all indoor units B, indoor units C, and hot water supply units F connected to the relay unit E by communication at the time of system startup.
  • FIG. 3 is a schematic diagram schematically showing a connection state in the hot water supply unit F of the refrigeration cycle apparatus 100 according to the embodiment of the present invention. Based on FIG. 3, the connection state in the hot water supply unit F will be described.
  • the hot water supply unit F is provided with a hot water storage tank 32.
  • the hot water storage tank 32 detects the temperature of a water supply valve 33 provided at a water supply port (not shown), a drain valve 34 provided at a water discharge port (not shown), and water and hot water stored in the hot water storage tank 32.
  • a water temperature sensor 35 for detecting the amount of water and hot water stored in the hot water storage tank 32 (water level) is provided.
  • the hot water supply unit controller 64 is connected to the water temperature sensor 35 and the water amount sensor 36, and can grasp the water temperature and the water amount of the hot water storage tank 32 based on information transmitted from these.
  • the hot water supply unit controller 64 is connected to the water supply valve 33 and controls the opening and closing of the water supply valve 33. That is, the hot water supply unit controller 64 can replenish cold water into the hot water storage tank 32 by opening the water supply valve 33.
  • the hot water supply unit controller 64 is connected to the drain valve 34 and controls the opening and closing of the drain valve 34. That is, the hot water supply unit controller 64 can discharge hot water outside the hot water storage tank 32 by opening the drain valve 34.
  • FIG. 4 is a flowchart showing a flow of communication / operation processing executed by the heat source unit controller 61. Based on FIG. 4, a flow of communication / operation processing executed by the heat source unit controller 61 will be described. Note that steps S100 to S106 shown in FIG. 4 show processing executed by the heat source unit controller 61.
  • the hot water supply unit F1 will be described as an example.
  • the user operates the remote controller 65 to set a set temperature for the hot water supply unit F1.
  • the user can set a binary set temperature.
  • the binary set temperature refers to the hot water supply temperature originally required by the hot water supply unit F1 (first set temperature) and the temperature at which the hot water supply unit F1 is automatically operated for the purpose of energy saving or continuation of stable operation of the entire system. (Second set temperature).
  • the second set temperature is set to a value higher than the first set temperature. For example, the user sets 55 ° C. as the first set temperature and 60 ° C. as the second set temperature.
  • the remote controller 65 stores the set binary set temperature in the memory and transmits it to the hot water supply unit controller 64 via the transmission line 9.
  • the hot water supply unit controller 64 that has received the set binary set temperature stores the received binary set temperature in a memory and transmits it to the relay unit controller 62 via the transmission line 8.
  • the binary set temperature is further transmitted to the centralized controller 66 via 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 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 should not set the second set temperature.
  • the user can also set the binary set temperature by operating the centralized controller 66.
  • the centralized controller 66 stores the set binary set temperature in a memory and transmits the temperature to the hot water supply unit controller 64 via the transmission line 10, the transmission line 7, and the transmission line 8.
  • the hot water supply unit controller 64 that has received the set binary set temperature transmits the received binary set temperature to the relay unit controller 62 via the transmission line 8, and further remotely via the transmission line 9.
  • the data is also transmitted to the controller 65.
  • the heat source unit controller 61 can own the automatic operation propriety information regarding all the hot water supply units F connected on the refrigerant circuit.
  • the heat source unit controller 61 performs newly received communication analysis processing (step S101).
  • the communication received here is the operation / stop state of all the indoor units B, indoor units C, and hot water supply units F connected on the refrigerant circuit, and whether or not automatic operation is possible.
  • the heat source unit controller 61 determines whether automatic operation is possible (step S102). For example, it is determined that automatic operation is possible when one or more hot water supply units F that can be automatically operated are stopped or are in automatic operation. This is because even if the hot water supply unit F is set to be capable of automatic operation, it can be assumed that the normal operation should not be stopped automatically when the normal operation is started by the user's operation.
  • step S102 When automatic operation is possible (step S102; Y), the heat source unit controller 61 operates / stops, pressure, temperature, compression of all indoor units B, indoor units C, and hot water supply units F connected on the refrigerant circuit.
  • the operating capacity, load state, system COP, etc. are analyzed from various data such as machine operating frequency and current (step S103). For example, the total capacity of the indoor unit B and the indoor unit C that are turned on in the cooling thermostat, the total capacity of the indoor unit B and the indoor unit C that is turned on in the heating thermostat, and the total capacity of the hot water supply unit F that is turned on in the thermostat The balance between the cooling load, the heating load and the hot water supply load is determined.
  • the heating load when the heating load is small without the cooling load and the compressor operating frequency is low, it can be determined that the heating is a small capacity operation, and when both the outside air temperature and the indoor temperature are high and the high pressure is high. It can be determined that the heating overload small capacity operation.
  • the heat source unit controller 61 determines whether or not the operation state can be improved by operating and stopping the hot water supply unit F capable of automatic operation (step S104). For example, when the cooling load is larger than the heating load and the hot water supply load, when the difference between the cooling load, the heating load and the hot water supply load is reduced by operating the hot water supply unit F that can be automatically operated, the hot water supply unit F is It can be determined that the system COP is improved by operating. Moreover, when the indoor unit C which carries out heating operation by the operation operation increases from that state, and the heating load and the hot water supply load become larger than the cooling load, the hot water supply unit F which is automatically operated is stopped. It can be determined that the system COP is improved while suppressing the switching from the cooling main operation to the heating main operation.
  • the heating small capacity operation state it can be determined that the motor efficiency of the air-conditioning compressor 101 is improved by operating the hot water supply unit F capable of automatic operation, and the energy saving operation is performed. Furthermore, from this state, when the number of indoor units C that perform heating operation increases due to operation, and the heating capacity increases, power consumption can be reduced by stopping the hot water supply unit F that is automatically operated. Can be determined. In the case of the heating overload small capacity operation, it can be determined that the high pressure can be reduced by operating the hot water supply unit F capable of automatic operation and the stable operation can be continued. Thereafter, when the high pressure is sufficiently reduced due to a change in the number of operating units, it can be determined that the power consumption can be reduced by stopping the hot water supply unit F that is automatically operated.
  • the hot water supply unit F to be changed is determined.
  • the priority order for example, a manual setting method in advance can be considered. This priority order may be set according to uses such as hotel rooms and employee rooms, for example. Alternatively, a method of setting the priority order according to the address of the hot water supply unit controller 64 is also possible. In this case, it can be realized by setting the numerical value of the address in ascending order or descending order according to the priority order.
  • the heat source unit controller 61 transmits information on the hot water supply unit F to be operated / stopped to the relay unit controller. It transmits to 62 (step S105). After the completion of the transmission process, the heat source unit controller 61 performs normal processes such as capturing of sensor input and actuator control (step S106). By the way, the heat source unit controller 61 determines that the operation state cannot be improved by operating / stopping the hot water supply unit F capable of automatic operation when it is determined that automatic operation is impossible (step S102; N). If this happens (step S104; N), normal processing is performed (step S106).
  • the relay unit controller 62 When the relay unit controller 62 receives the automatic operation / stop command for the hot water supply unit F from the heat source unit controller 61, the relay unit controller 62 transmits the automatic operation / stop command to the target hot water supply unit controller 64. When the relay unit controller 62 receives a change in the operation state from the indoor unit controller 63 or the hot water supply unit controller 64, the relay unit controller 62 transmits the change in the operation state to the heat source unit controller 61.
  • the hot water supply unit controller 64 When the hot water supply unit controller 64 receives the automatic operation / stop command from the relay unit controller 62, the hot water supply unit controller 64 changes the operation state according to the command, and transmits the change in the operation state to the remote controller 65 and the centralized controller 66.
  • the hot water supply unit controller 64 receives a normal operation / stop command from the remote controller 65 or the centralized controller 66, the hot water supply unit controller 64 changes the operation state according to the command and transmits the change in the operation state to the relay unit controller 62. Further, the hot water supply unit controller 64 identifies and holds its own operation state as normal operation and automatic operation, and also identifies and transmits the information to the remote controller 65 and the centralized controller 66.
  • the hot water supply unit controller 64 is operated for the purpose of causing the water temperature to reach the first set temperature in the normal operation, and when the water temperature reaches the first set temperature, the thermostat is turned off. Continues the thermo-ON until the water temperature reaches the second set temperature. This is because the hot water supply unit F can be continuously operated for a long time for the purpose of energy saving of the entire system or continuation of stable operation.
  • the water supply valve 33 is opened, the cold water is replenished to lower the water temperature, and the operation is continued.
  • this cold water discharge control can be selected by separately providing a priority order determination means for continuing automatic operation.
  • the remote controller 65 and the centralized controller 66 When the remote controller 65 and the centralized controller 66 receive a change in the automatic operation / stop state from the hot water supply unit controller 64, the remote controller 65 and the centralized controller 66 recognize the information and reflect it in the display. At this time, regarding the display, normal operation and automatic operation may be identified and displayed. The purpose is to make the user recognize that automatic driving is being performed, and to distinguish it from forgetting to turn off the remote controller (remote controller 65). Further, when the user performs operation / stop by the user, the remote controller 65 and the centralized controller 66 recognize the information, reflect the information on the display, and transmit the information to the hot water supply unit controller 64.
  • the means for operating the hot water supply unit F is provided in the heat source unit controller 61 as an example in FIG. 4, other means for operating the hot water supply unit F may be provided.
  • the heat source unit controller 61 is provided with means for operating the hot water supply unit F
  • the heat source unit A can perform control judgment using data such as its own pressure, temperature, compressor operating frequency, and current. The amount of communication can be suppressed.
  • the centralized controller 66 with means for operating the hot water supply unit F. The advantage of this method is that an optimum operation schedule of the hot water supply unit F can be predicted and created by making a determination using schedule setting information of the entire system held by the centralized controller 66.
  • the indoor unit controller 63 with means for operating the hot water supply unit F.
  • An advantage of this method is that it can be controlled by a simple algorithm such as operating / stopping the hot water supply unit F in conjunction with the operation / stopping of the indoor unit B and the indoor unit C. It is also possible to provide the hot water supply unit controller 64 itself with means for operating the hot water supply unit F. An advantage of this method is that the hot water supply unit F can contribute to energy saving while suppressing changes in the water temperature by autonomous control.
  • the hot water supply load when the cooling load is larger than the heating load and the hot water supply load, the hot water supply load is operated to improve the system COP and realize energy saving while running. Costs can be reduced. Further, according to the refrigeration cycle apparatus 100, it is possible to improve the motor efficiency of the air-conditioning compressor 101 by operating the hot water supply load during the heating and small capacity operation, further reducing energy consumption and reducing running cost. It becomes. Further, according to the refrigeration cycle apparatus 100, when the heating overload and small capacity operation is performed, the hot water supply load is operated, so that the high pressure can be reduced and the stable operation can be continued.
  • the refrigeration cycle apparatus 100 in which the secondary refrigerant (hot water) of the hot water supply unit F is used as a heat storage medium has been described as an example.
  • the configuration of the refrigeration cycle apparatus 100 is limited to this. is not.
  • an air conditioner as shown in FIG. 5 (with a system in which heat is transferred from the direct expansion air conditioning to another secondary refrigerant) can be considered in the same manner.
  • the case where there is a hot water supply unit F has been described as an example. However, even if there is no hot water supply unit F, the air conditioning load of the indoor unit B and the entire indoor unit C may be balanced. Needless to say.
  • FIG. 5 is a refrigerant circuit diagram showing another example of the refrigerant circuit configuration of the refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100A) according to the embodiment of the present invention. Based on FIG. 5, the refrigerant circuit configuration and operation of the refrigeration cycle apparatus 100A will be described.
  • FIG. 5 shows an example in which the refrigeration cycle apparatus 100A is an air conditioner that can simultaneously supply a cooling load and a heating load (or hot water supply load) by using a refrigeration cycle that circulates a refrigerant (heat source refrigerant). It shows.
  • the difference from FIG. 1 will be mainly described, and the same parts as those in FIG. 1 will be denoted by the same reference numerals and the description thereof will be omitted.
  • a heat source unit A and a relay unit (hereinafter referred to as a relay unit E1) are connected via a heat exchanger related to heat medium 71a and a heat exchanger related to heat medium 71b provided in the relay unit E1.
  • the refrigerant pipes 5 (the high-pressure side connection pipe 106 and the low-pressure side connection pipe 107) are connected.
  • the relay unit E1 and the indoor unit (hereinafter referred to as indoor unit B1) are also connected by the refrigerant pipe 6 via the heat exchanger related to heat medium 71a and the heat exchanger related to heat medium 71b. Note that all the indoor units shown in FIG. 5 are referred to as an indoor unit B1 for convenience.
  • An indoor heat exchanger 118 is mounted on each of the indoor units B1. That is, the indoor unit B1 is different from the indoor unit B in that the air conditioning throttle means 117 is not mounted.
  • the indoor heat exchanger 118 is connected to the heat medium flow control device 75 and the second heat medium flow switching device 76 of the relay unit E1 by the refrigerant pipe 6.
  • FIG. 5 shows an example in which four indoor units B1 are connected to the relay unit E1, but the number of indoor units B1 connected is not limited to four.
  • the relay unit E1 includes two heat exchangers for heat medium 71, two expansion devices 72, two switching devices 73, two second refrigerant flow switching devices 74, two pumps 80, 4 Two first heat medium flow switching devices 77, four second heat medium flow switching devices 76, and four heat medium flow control devices 75 are mounted.
  • the two heat exchangers between heat media 71 function as a condenser (heat radiator) or an evaporator, and heat is generated by the heat source side refrigerant and the heat medium. Exchange is performed, and the cold or warm heat generated in the heat source unit A and stored in the heat source side refrigerant is transmitted to the heat medium.
  • the heat exchanger related to heat medium 71a is provided between the expansion device 72a and the second refrigerant flow switching device 74a, and serves to cool the heat medium in the cooling / heating mixed operation mode.
  • the heat exchanger related to heat medium 71b is provided between the expansion device 72b and the second refrigerant flow switching device 74b, and serves to heat the heat medium in the cooling / heating mixed operation mode.
  • the two expansion devices 72 have functions as a pressure reducing valve and an expansion valve, and expand the heat source side refrigerant by reducing the pressure.
  • the expansion device 72a is provided on the upstream side of the heat exchanger related to heat medium 71a in the flow of the heat source side refrigerant during the cooling operation.
  • the expansion device 72b is provided on the upstream side of the heat exchanger related to heat medium 71b in the flow of the heat source side refrigerant during the cooling operation.
  • the two throttling devices 72 may be configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.
  • the two opening / closing devices 73 are configured by two-way valves or the like and open / close the refrigerant pipe 5.
  • the opening / closing device 73a is provided in the refrigerant pipe 5 on the inlet side of the heat source side refrigerant.
  • the switchgear 73b is provided in a pipe connecting the refrigerant pipe 5 on the inlet side and outlet side of the heat source side refrigerant.
  • the two second refrigerant flow switching devices 74 are configured by four-way valves or the like, and switch the flow of the heat source side refrigerant according to the operation mode. Is.
  • the second refrigerant flow switching device 74a is provided on the downstream side of the heat exchanger related to heat medium 71a in the flow of the heat source side refrigerant during the cooling operation.
  • the second refrigerant flow switching device 74b is provided on the downstream side of the heat exchanger related to heat medium 71b in the flow of the heat source side refrigerant during the cooling only operation.
  • the two pumps 80 (pump 80a and pump 80b) circulate a heat medium that is conducted through the refrigerant pipe 6.
  • the pump 80 a is provided in the refrigerant pipe 6 between the heat exchanger related to heat medium 71 a and the second heat medium flow switching device 76.
  • the pump 80 b is provided in the refrigerant pipe 6 between the heat exchanger related to heat medium 71 b and the second heat medium flow switching device 76.
  • the two pumps 80 may be constituted by, for example, pumps capable of capacity control.
  • the four first heat medium flow switching devices 77 are configured by a three-way valve or the like, and switch the flow path of the heat medium.
  • the number of first heat medium flow switching devices 77 is set according to the number of indoor units B1 installed (here, four).
  • one of the three sides is in the heat exchanger 71a, one of the three is in the heat exchanger 71b, and one of the three is in the heat medium flow rate.
  • Each is connected to the adjusting device 75 and provided on the outlet side of the heat medium flow path of the indoor heat exchanger 118.
  • the four second heat medium flow switching devices 76 are configured by a three-way valve or the like, and switch the flow path of the heat medium.
  • the number of the second heat medium flow switching devices 76 is set according to the number of indoor units B installed (here, four).
  • one of the three sides is in the heat exchanger 71a, one of the three is in the heat exchanger 71b, and one of the three is indoor heat exchange.
  • the four heat medium flow control devices 75 are configured by, for example, a two-way valve using a stepping motor, and the like, and the opening degree of the refrigerant pipe 6 serving as the heat medium flow path can be changed to adjust the flow rate of the heat medium. Is.
  • the number of heat medium flow control devices 75 (four in this case) according to the number of installed indoor units B1 is provided.
  • One of the heat medium flow control devices 75 is connected to the indoor heat exchanger 118 and the other is connected to the first heat medium flow switching device 77, and is provided on the outlet side of the heat medium flow channel of the indoor heat exchanger 118.
  • the heat medium flow control device 75 may be provided on the inlet side of the heat medium flow path of the indoor heat exchanger 118.
  • the heat source unit A and the relay unit E1 are connected via the heat exchanger related to heat medium 71a and the heat exchanger related to heat medium 71b provided in the relay unit E1, and the relay unit E1.
  • the indoor unit B1 are also connected via a heat exchanger related to heat medium 71a and a heat exchanger related to heat medium 71b. That is, in the refrigeration cycle apparatus 100A, the heat source side refrigerant circulating in the air conditioning refrigeration cycle 1 and the heat medium circulation circuit (for example, for hot water supply described in FIG. 1) in the heat exchanger related to heat medium 71a and the heat exchanger related to heat medium 71b. Heat is exchanged with the heat medium circulating in the refrigeration cycle 2).
  • the refrigeration cycle apparatus 100A configured as described above, when the cooling load is large with respect to the heating load (or hot water supply load), operating the hot water supply load improves the system COP and realizes energy saving. However, the running cost can be reduced. Further, according to the refrigeration cycle apparatus 100A, by operating a heating load (or hot water supply load) at the time of heating small capacity operation, the motor efficiency of the air-conditioning compressor 101 is improved and energy saving is further realized while running cost is reduced. It becomes possible to reduce. Further, according to the refrigeration cycle apparatus 100A, when the heating overload and small capacity operation is performed, the high pressure can be reduced and the stable operation can be continued by operating the heating load (or hot water supply load).

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Air Conditioning Control Device (AREA)
PCT/JP2009/006177 2009-11-18 2009-11-18 冷凍サイクル装置及びそれに適用される情報伝達方法 WO2011061792A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP09851418.5A EP2503266B1 (de) 2009-11-18 2009-11-18 Kältekreislaufvorrichtung und daran adaptierte informationsverbreitungsverfahren
JP2011541733A JP5642085B2 (ja) 2009-11-18 2009-11-18 冷凍サイクル装置及びそれに適用される情報伝達方法
PCT/JP2009/006177 WO2011061792A1 (ja) 2009-11-18 2009-11-18 冷凍サイクル装置及びそれに適用される情報伝達方法
CN200980162495.5A CN102695929B (zh) 2009-11-18 2009-11-18 冷冻循环装置及适用于该冷冻循环装置的信息传递方法
US13/510,150 US20120222440A1 (en) 2009-11-18 2009-11-18 Regrigeration cycle apparatus and information transfer method used therein

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/006177 WO2011061792A1 (ja) 2009-11-18 2009-11-18 冷凍サイクル装置及びそれに適用される情報伝達方法

Publications (1)

Publication Number Publication Date
WO2011061792A1 true WO2011061792A1 (ja) 2011-05-26

Family

ID=44059296

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/006177 WO2011061792A1 (ja) 2009-11-18 2009-11-18 冷凍サイクル装置及びそれに適用される情報伝達方法

Country Status (5)

Country Link
US (1) US20120222440A1 (de)
EP (1) EP2503266B1 (de)
JP (1) JP5642085B2 (de)
CN (1) CN102695929B (de)
WO (1) WO2011061792A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013061399A1 (ja) * 2011-10-24 2013-05-02 三菱電機株式会社 ヒートポンプシステム、制御装置、温調方法及びプログラム
EP2781848A4 (de) * 2011-09-29 2015-06-24 Mitsubishi Electric Corp Kombiniertes klimaanlagen-/heisswasserversorgungssystem

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5404333B2 (ja) * 2009-11-13 2014-01-29 三菱重工業株式会社 熱源システム
US9562696B2 (en) * 2010-04-15 2017-02-07 Mitsubishi Electric Corporation Hot water supply system control apparatus and hot water supply system control program and hot water supply system operating method
KR101212698B1 (ko) * 2010-11-01 2013-03-13 엘지전자 주식회사 히트 펌프식 급탕장치
KR101203579B1 (ko) * 2010-11-05 2012-11-21 엘지전자 주식회사 공조 겸용 급탕 장치 및 그 운전방법
WO2013136368A1 (ja) * 2012-03-15 2013-09-19 三菱電機株式会社 冷凍サイクル装置
JP5911590B2 (ja) * 2012-10-10 2016-04-27 三菱電機株式会社 空気調和装置
WO2014091548A1 (ja) * 2012-12-11 2014-06-19 三菱電機株式会社 空調給湯複合システム
US9933192B2 (en) * 2012-12-20 2018-04-03 Mitsubishi Electric Corporation Air-conditioning apparatus
US10451306B2 (en) * 2014-07-28 2019-10-22 Mitsubishi Electric Corporation Air-conditioning apparatus
US10775056B2 (en) * 2014-09-08 2020-09-15 United Maintenance, Inc. Natatorium dehumidifier
EP3260690A4 (de) 2015-02-16 2018-10-17 Volvo Construction Equipment AB Drehmomentsteuerungssystem für dpf-regenerierung
CN111486613B (zh) * 2020-04-29 2022-05-20 广东美的暖通设备有限公司 空调系统及其控制方法和装置、存储介质
CN114992693A (zh) * 2021-03-01 2022-09-02 艾欧史密斯(中国)热水器有限公司 热泵机组及其控制方法、控制装置、热泵系统、联供系统
EP4227605A1 (de) * 2022-02-11 2023-08-16 Daikin Europe N.V. Kühlvorrichtung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0250056A (ja) * 1988-08-10 1990-02-20 Daikin Ind Ltd 熱回収形空気調和装置
JPH09119736A (ja) * 1995-10-24 1997-05-06 Sanyo Electric Co Ltd 多室型冷暖房装置及びその運転方法
JPH11270920A (ja) 1998-03-20 1999-10-05 Mitsubishi Electric Corp 多機能ヒートポンプシステムおよびその運転制御方法
JP2007232232A (ja) * 2006-02-27 2007-09-13 Sanyo Electric Co Ltd 冷却加熱装置
WO2009122477A1 (ja) * 2008-03-31 2009-10-08 三菱電機株式会社 空調給湯複合システム

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5512372A (en) * 1978-07-11 1980-01-28 Daikin Ind Ltd Multi-chamber type air conditioner
JPH0633899B2 (ja) * 1985-07-02 1994-05-02 三菱電機株式会社 空気調和機の集中監視装置
JPS6334459A (ja) * 1986-07-29 1988-02-15 株式会社東芝 空気調和機
GB2215867B (en) * 1988-02-09 1992-09-02 Toshiba Kk Air conditioner system with control for optimum refrigerant temperature
JP2909187B2 (ja) * 1990-10-26 1999-06-23 株式会社東芝 空気調和機
JPH07225064A (ja) * 1994-02-15 1995-08-22 Hitachi Ltd ヒートポンプ給湯装置
JP3643629B2 (ja) * 1995-11-30 2005-04-27 三洋電機株式会社 空気調和システムにおける自動運転設定方法及び空気調和システム
US6848267B2 (en) * 2002-07-26 2005-02-01 Tas, Ltd. Packaged chilling systems for building air conditioning and process cooling
JP2001280749A (ja) * 2000-03-31 2001-10-10 Daikin Ind Ltd 冷凍装置
WO2002046663A1 (fr) * 2000-12-08 2002-06-13 Daikin Industries, Ltd. Refrigerateur
EP1275913A3 (de) * 2001-06-26 2003-08-13 Mitsubishi Heavy Industries, Ltd. Vielförmige Klimaanlage der Art einer Gaswärmepumpe
KR100569554B1 (ko) * 2002-03-29 2006-04-10 다이킨 고교 가부시키가이샤 공기 조화 장치의 열원 유닛 및 공기 조화 장치
JP3956784B2 (ja) * 2002-07-04 2007-08-08 ダイキン工業株式会社 冷凍装置
JP2005300006A (ja) * 2004-04-12 2005-10-27 Hitachi Ltd マルチ型空気調和機
JP3781046B2 (ja) * 2004-07-01 2006-05-31 ダイキン工業株式会社 空気調和装置
JP3984250B2 (ja) * 2004-09-27 2007-10-03 三星電子株式会社 多室型空気調和機
US8033479B2 (en) * 2004-10-06 2011-10-11 Lawrence Kates Electronically-controlled register vent for zone heating and cooling
JP2006283989A (ja) * 2005-03-31 2006-10-19 Sanyo Electric Co Ltd 冷暖房システム
JP2007139265A (ja) * 2005-11-16 2007-06-07 Mitsubishi Heavy Ind Ltd マルチ型空気調和機の運転制御方法およびプログラム

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0250056A (ja) * 1988-08-10 1990-02-20 Daikin Ind Ltd 熱回収形空気調和装置
JPH09119736A (ja) * 1995-10-24 1997-05-06 Sanyo Electric Co Ltd 多室型冷暖房装置及びその運転方法
JPH11270920A (ja) 1998-03-20 1999-10-05 Mitsubishi Electric Corp 多機能ヒートポンプシステムおよびその運転制御方法
JP2007232232A (ja) * 2006-02-27 2007-09-13 Sanyo Electric Co Ltd 冷却加熱装置
WO2009122477A1 (ja) * 2008-03-31 2009-10-08 三菱電機株式会社 空調給湯複合システム

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2781848A4 (de) * 2011-09-29 2015-06-24 Mitsubishi Electric Corp Kombiniertes klimaanlagen-/heisswasserversorgungssystem
WO2013061399A1 (ja) * 2011-10-24 2013-05-02 三菱電機株式会社 ヒートポンプシステム、制御装置、温調方法及びプログラム
CN103890502A (zh) * 2011-10-24 2014-06-25 三菱电机株式会社 热泵系统、控制装置、调温方法以及程序
JPWO2013061399A1 (ja) * 2011-10-24 2015-04-02 三菱電機株式会社 ヒートポンプシステム、制御装置、温調方法及びプログラム
US9644872B2 (en) 2011-10-24 2017-05-09 Mitsubishi Electric Corporation Heat pump system, control device, temperature adjustment method, and program

Also Published As

Publication number Publication date
EP2503266A1 (de) 2012-09-26
JPWO2011061792A1 (ja) 2013-04-04
EP2503266B1 (de) 2018-10-24
US20120222440A1 (en) 2012-09-06
JP5642085B2 (ja) 2014-12-17
EP2503266A4 (de) 2016-10-05
CN102695929B (zh) 2014-07-30
CN102695929A (zh) 2012-09-26

Similar Documents

Publication Publication Date Title
JP5642085B2 (ja) 冷凍サイクル装置及びそれに適用される情報伝達方法
JP5121922B2 (ja) 空調給湯複合システム
JP5084903B2 (ja) 空調給湯複合システム
US9285128B2 (en) Air-conditioning apparatus with multiple outdoor, indoor, and multiple relay units
EP2527751B1 (de) Kombinationssystem aus heisswasserversorgung und klimaanlage
KR101391775B1 (ko) 히트 펌프 시스템
CN103229006B (zh) 供热水空调复合装置
JP5627606B2 (ja) ヒートポンプシステム
WO2010098070A1 (ja) ヒートポンプシステム
JPWO2009098751A1 (ja) 空調給湯複合システム
CN101438109A (zh) 可变容量多回路空调系统
JP5264936B2 (ja) 空調給湯複合システム
WO2008113121A1 (en) A thermal transfer, recovery and management system
EP2584285B1 (de) Kälte-klimaanlage
US20210207834A1 (en) Air-conditioning system
JP2001074331A (ja) 空気調和機の室外ユニットおよびこの室外ユニットを用いた空気調和システム
JP5642270B2 (ja) 空気調和装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09851418

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2011541733

Country of ref document: JP

WWE Wipo information: entry into national phase

Ref document number: 2009851418

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 13510150

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE