WO2010109619A1 - Unité de relais côté charge et système composé d'alimentation en eau chaude/conditionnement d'air sur lequel l'unité de relais côté charge est montée - Google Patents

Unité de relais côté charge et système composé d'alimentation en eau chaude/conditionnement d'air sur lequel l'unité de relais côté charge est montée Download PDF

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Publication number
WO2010109619A1
WO2010109619A1 PCT/JP2009/056049 JP2009056049W WO2010109619A1 WO 2010109619 A1 WO2010109619 A1 WO 2010109619A1 JP 2009056049 W JP2009056049 W JP 2009056049W WO 2010109619 A1 WO2010109619 A1 WO 2010109619A1
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Prior art keywords
refrigerant
hot water
water supply
load
air
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PCT/JP2009/056049
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English (en)
Japanese (ja)
Inventor
宏典 薮内
純一 亀山
博文 ▲高▼下
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2009/056049 priority Critical patent/WO2010109619A1/fr
Priority to JP2011505742A priority patent/JPWO2010109619A1/ja
Publication of WO2010109619A1 publication Critical patent/WO2010109619A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

Definitions

  • the present invention relates to a load-side relay unit that houses a plurality of heat exchangers and an air-conditioning and hot-water supply complex system equipped with the same.
  • a heat source unit equipped with a first compressor, a flow path switching valve, a heat source side heat exchanger, a first flow control device, a first load side heat exchanger, A first load-side unit including a two-compressor, a second load-side heat exchanger, and a second flow rate control device, the first compressor, the flow path switching valve, and the heat source-side heat.
  • the exchanger, the first flow control device, and the first load-side heat exchanger are sequentially connected by a refrigerant pipe to form a main circuit, and the second compressor and the second load-side heat exchange.
  • a heat pump device is proposed in which a load-side refrigerant circuit is configured by sequentially connecting a condenser, the second flow rate control device, and the first load-side heat exchanger with refrigerant piping (see, for example, Patent Document 1). ).
  • the heat pump device described in Patent Document 1 is provided with a load-side refrigerant circuit, whereby the capacity of the main circuit can be enhanced and the operation efficiency is improved.
  • various refrigeration devices constituting the load-side refrigerant circuit are mounted on a load-side unit (conceived by the load-side relay unit according to the present invention).
  • the load-side unit includes a control board that uses an inverter as a drive source such as a hot water compressor or a fan motor. In such a case, it is necessary to cool the control board in order to protect the control board from the heat generated by the inverter.
  • a cooling air passage for supplying cooling air to the control board is provided in the unit. If it is a normal unit (for example, indoor unit etc.), since the air passage space is secured, it does not matter so much.
  • a load side unit as described in Patent Document 1 a plurality of heat exchangers (first load side heat exchanger and second load side heat exchanger) are mounted, and a hot water supply compressor, Since a fan motor or the like is also mounted, there remains a problem that internal space is greatly restricted in forming the cooling air passage.
  • the present invention has been made in order to solve the above-described problem.
  • the load-side relay unit accommodates a plurality of heat exchangers and a control board and has an optimum air path design, and an air-conditioning hot water supply equipped with the load-side relay unit. It aims to provide a complex system.
  • the load-side relay unit according to the present invention is equipped with at least two heat exchangers and a control board, and exhausts air that sucks air for cooling the control board and air that has cooled the control board.
  • a load-side relay unit of a refrigeration cycle apparatus in which an exhaust port is formed, wherein the intake port is formed on a bottom surface and the exhaust port is formed above a side surface.
  • 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 for circulating hot water supply refrigerant in the refrigerant circuit, a water circulation pump, the heat medium-refrigerant heat exchanger, and a water circuit in which a hot water storage tank is connected in series, the hot water supply water in the water circuit Hot water supply load that circulates
  • the load side relay unit According to the load side relay unit according to the present invention, it is possible to design an optimum air path according to the realization of downsizing.
  • 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.
  • 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.
  • a load-side relay unit F is mounted on the air conditioning and hot water supply complex system 100 (described in detail in FIG. 2). In FIG.
  • 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 throttle means 119 and a refrigerant-refrigerant heat exchanger 41 connected in series. 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 one or more 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.
  • the load-side relay unit F includes 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. Contained. In other words, the load-side relay unit F has a part of the air-conditioning refrigeration cycle 1 through the refrigerant-refrigerant heat exchanger 41, the whole hot water supply refrigeration cycle 2, and the heat medium-refrigerant heat exchanger 51. A part of the hot water supply load 3 is accommodated.
  • the load-side relay unit F includes a control board that uses an inverter as a drive source for the hot water supply compressor 21 and a fan motor (not shown) (see FIG. 4).
  • the load-side relay unit F tends to be large because a plurality of heat exchangers (refrigerant-refrigerant heat exchanger 41 and heat medium-refrigerant heat exchanger 51) are accommodated. Therefore, in the load-side relay unit F according to the present embodiment, the load-side relay unit F is miniaturized as described below, and an optimal air path is formed inside to efficiently control the control board. It can be cooled.
  • FIG. 2 is an enlarged circuit diagram showing an enlarged portion of the load side relay unit F according to the embodiment of the present invention.
  • FIG. 3 is a perspective external view schematically showing the external appearance of the load-side relay unit F.
  • FIG. 4 is an exploded perspective view schematically showing a state in which the control board is disassembled.
  • FIG. 5 is an explanatory diagram for explaining the flow of air in the load-side relay unit F.
  • the load-side relay unit F includes a hot water supply compressor 21, a refrigerant-refrigerant heat exchanger 41, a heat medium-refrigerant heat exchanger 51, a hot water supply throttle means 22, and a hot water supply heat source throttle.
  • a means 119 is accommodated.
  • the load-side relay unit F houses the refrigerant-refrigerant heat exchanger 41, the hot water supply heat source throttle means 119, the heat medium-refrigerant heat exchanger 51, the hot water supply compressor 21, and the hot water supply throttle means 22. It has a function as a housing.
  • an intake port 60 is formed at a part of the bottom surface, and an exhaust port 61 is formed at a part above the side surface. That is, in the load-side relay unit F, air is sucked in from the intake port 60 by a blower (not shown), guided upward inside, and exhausted from the exhaust port 61.
  • the exhaust port 61 is formed in the vicinity of an inverter cooler 25d described later.
  • the control board 25 is usually composed of a main board 25a on which a control circuit and the like are mounted, a relay board 25b, a high-power part 25c, and an inverter cooler 25d.
  • the high power unit 25c and the inverter cooler 25d are provided on one substrate (hereinafter referred to as a heat sink substrate).
  • these substrates are arranged and mounted in a plane. If it does so, the internal volume of the load side relay unit F must be enlarged, and it cannot reduce in size. Therefore, the control board 25 is mounted such that the main board 25a, the relay board 25b, and the heat sink board are sequentially stacked from the left side of the drawing. By doing so, the length and height of the control board 25 are shortened.
  • control board 25 is installed so that the main board 25a is on the front side of the load-side relay unit F. Therefore, the main board 25a can be maintained simply by opening a cover (not shown) provided on the front side of the load-side relay unit F, thereby facilitating maintenance.
  • the high-power portion 25c is installed on the rear rear side of the relay board 25b, it is possible to reduce the danger to the worker during maintenance.
  • the control board 25 ⁇ By making the control board 25 a laminated structure, it is possible to facilitate the replacement work of the components inside the load-side relay unit F.
  • the set of the control box can be removed by removing the screws fixing the control box in which the control board 25 is accommodated, and the hot water supply compressor can be easily removed. 21 can be exchanged. Therefore, even when the load-side relay unit F is installed in a narrow space such as a washroom and the space for maintenance is very small, it can be easily attached and detached in units of control boxes, so that maintenance work efficiency is improved. There is no worsening.
  • the load side relay unit F is formed with the intake port 60 on the bottom surface and the exhaust port 61 on the side surface.
  • the air paths (air path A and air path B) formed in the load-side relay unit F are indicated by arrows. Specifically, the flow of air in the load-side relay unit F will be described.
  • the cooling air sucked by the fan from the intake port 60 is conducted through the air path A.
  • this cooling air is guided upward inside and conducts the air path B formed in the heat sink board. This cooling air cools the high voltage section 25c and the inverter cooler 25d, and then is exhausted together with heat to the outside of the load side relay unit F through the exhaust port 61.
  • the air inlets of such units are formed symmetrically with respect to the air outlets formed on one side of the cooling path.
  • both the downsizing and the cooling efficiency are achieved by forming the intake port and the exhaust port at symmetrical positions. Feasibility is low. Therefore, in the load-side relay unit F, as shown in FIG. 2, the intake port 60 is formed in the lower part and the exhaust port 61 is formed in the upper part of the side surface (near the inverter cooler 25d).
  • the noise that leaks outside through the air intake port 60 can be reduced by forming the air intake port 60 in the lower part instead of forming it on the side surface of the load-side relay unit F. Further, by forming the intake port 60 at the lower part of the load-side relay unit F, the intake port 60 is surrounded by a housing leg portion (not shown), and the amount of suction of dust and the like that is sucked together with the suction of air. Can also be reduced.
  • the opening area of the exhaust port 61 is set so that the wind speed of the air passing through the inverter cooler 25d is optimized.
  • the exhaust port 61 is composed of a plurality of small openings. By doing so, it is possible to optimize the wind speed of the cooling air conducted to the inverter cooler 25d and to suppress the invasion of insects. If insects enter the load-side relay unit F, there is a possibility that an electrical circuit provided on the control board 25 may be short-circuited or an unexpected injury may occur when an operator inadvertently puts a finger or the like. Therefore, the intrusion of insects can be suppressed by configuring the exhaust port 61 with a plurality of small openings. For example, it is good to avoid the slight gap (generally 3 mm or less) preferred by cockroaches or the like and to form the opening with a diameter of 3 mm or more and 4 mm or less.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'invention concerne une unité de relais côté charge qui héberge plusieurs échangeurs thermiques et un panneau de commande et qui possède un conduit d'air conçu de manière optimale, ainsi qu'un système composé d'alimentation en eau chaude/conditionnement d'air sur lequel l'unité de relais côté charge est montée. Au moins deux échangeurs thermiques (un échangeur thermique réfrigérant-réfrigérant (41), un échangeur thermique caloporteur-réfrigérant (51)) et un panneau de commande (25) sont montés sur l'unité (F) de relais côté charge. Une ouverture d'admission (60) destinée à aspirer l'air afin de refroidir le panneau de commande (25) et une ouverture d'échappement (61) destinée à décharger l'air ayant refroidi le panneau de commande (25) sont formées, l'ouverture d'admission (60) étant formée dans la base et l'ouverture d'échappement (61) au niveau de la partie supérieure de la surface latérale.
PCT/JP2009/056049 2009-03-26 2009-03-26 Unité de relais côté charge et système composé d'alimentation en eau chaude/conditionnement d'air sur lequel l'unité de relais côté charge est montée WO2010109619A1 (fr)

Priority Applications (2)

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PCT/JP2009/056049 WO2010109619A1 (fr) 2009-03-26 2009-03-26 Unité de relais côté charge et système composé d'alimentation en eau chaude/conditionnement d'air sur lequel l'unité de relais côté charge est montée
JP2011505742A JPWO2010109619A1 (ja) 2009-03-26 2009-03-26 負荷側中継ユニット及びそれを搭載した空調給湯複合システム

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PCT/JP2009/056049 WO2010109619A1 (fr) 2009-03-26 2009-03-26 Unité de relais côté charge et système composé d'alimentation en eau chaude/conditionnement d'air sur lequel l'unité de relais côté charge est montée

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CN104359247A (zh) * 2014-11-08 2015-02-18 合肥天鹅制冷科技有限公司 一种热泵装置
JP5954511B1 (ja) * 2016-03-04 2016-07-20 富士電機株式会社 ヒートポンプ式蒸気生成装置
JP2017015381A (ja) * 2015-06-29 2017-01-19 パナソニックＩｐマネジメント株式会社 空気調和機の室外機
EP2629022A4 (fr) * 2010-10-12 2018-04-04 Mitsubishi Electric Corporation Convertisseur de substance de chauffage et appareil climatiseur comportant le convertisseur de substance de chauffage
KR20190134181A (ko) * 2018-05-25 2019-12-04 엘지전자 주식회사 실외 유닛

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WO2008117408A1 (fr) * 2007-03-27 2008-10-02 Mitsubishi Electric Corporation Dispositif de pompe à chaleur

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JP2006118793A (ja) * 2004-10-21 2006-05-11 Denso Corp 給湯装置用電子制御装置
JP4816089B2 (ja) * 2006-01-12 2011-11-16 パナソニック株式会社 ヒートポンプ給湯機

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JPS63142621U (fr) * 1987-03-12 1988-09-20
JP2003106569A (ja) * 2001-09-27 2003-04-09 Toshiba Kyaria Kk 空気調和機の室外ユニット
WO2008117408A1 (fr) * 2007-03-27 2008-10-02 Mitsubishi Electric Corporation Dispositif de pompe à chaleur

Cited By (6)

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Publication number Priority date Publication date Assignee Title
EP2629022A4 (fr) * 2010-10-12 2018-04-04 Mitsubishi Electric Corporation Convertisseur de substance de chauffage et appareil climatiseur comportant le convertisseur de substance de chauffage
CN104359247A (zh) * 2014-11-08 2015-02-18 合肥天鹅制冷科技有限公司 一种热泵装置
JP2017015381A (ja) * 2015-06-29 2017-01-19 パナソニックＩｐマネジメント株式会社 空気調和機の室外機
JP5954511B1 (ja) * 2016-03-04 2016-07-20 富士電機株式会社 ヒートポンプ式蒸気生成装置
KR20190134181A (ko) * 2018-05-25 2019-12-04 엘지전자 주식회사 실외 유닛
KR102509997B1 (ko) 2018-05-25 2023-03-15 엘지전자 주식회사 실외 유닛

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