WO2010109620A1 - 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
WO2010109620A1
WO2010109620A1 PCT/JP2009/056054 JP2009056054W WO2010109620A1 WO 2010109620 A1 WO2010109620 A1 WO 2010109620A1 JP 2009056054 W JP2009056054 W JP 2009056054W WO 2010109620 A1 WO2010109620 A1 WO 2010109620A1
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WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
hot water
load
water supply
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Application number
PCT/JP2009/056054
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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/JP2009/056054 priority Critical patent/WO2010109620A1/fr
Priority to JP2011505743A priority patent/JP5202726B2/ja
Publication of WO2010109620A1 publication Critical patent/WO2010109620A1/fr

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    • 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
    • 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
    • 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). Since a plurality of heat exchangers (first load side heat exchanger and second load side heat exchanger) are connected to the load side refrigerant circuit, the size (size) of the load side unit (housing) is determined. It is expected to grow. If it does so, installation space will be restrict
  • the present invention has been made in order to solve the above-described problems, and accommodates a plurality of heat exchangers, and is designed to reduce the size and simplify the piping work, and an air conditioner equipped with the load-side relay unit. It aims to provide a hot water supply complex system.
  • the load-side relay unit according to the present invention is a load-side relay unit of a refrigeration cycle apparatus in which at least two heat exchangers are mounted, and the two or more heat exchangers are configured in substantially the same shape. It is characterized by being arranged so that the joint formation surfaces of the pipes connecting each other face each other.
  • 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 heat exchangers having substantially the same shape are arranged so that the joint forming surfaces of the pipes connecting each other face each other. It can be shortened, and simplification of piping construction and reduction in unit size can be realized.
  • the piping can be shortened accordingly, and simplification and downsizing of the piping work can be realized.
  • 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 a compressor 101 for air conditioning, a four-way valve 102 that is a flow path switching unit, an outdoor heat exchanger 103, and an accumulator 104 in series. It has the function of supplying cold heat to the cooling indoor unit B, the heating indoor unit C, and the hot water supply heat source circuit D.
  • 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 rotation speed can be variably controlled by an inverter, or may be configured as a type in which the rotation 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, the accumulator The process returns to the air conditioning compressor 101 via 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 rotational speed can be variably controlled by an inverter, or may be configured as a type in which the rotational 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. This load-side relay unit F tends to be large because a plurality of heat exchangers are accommodated. Therefore, in the present embodiment, as described below, the load-side relay unit F is miniaturized and piping construction is simplified.
  • 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 an enlarged perspective view showing a lower portion of the load side relay unit F in an enlarged manner.
  • FIG. 4 is an enlarged perspective view showing the heat exchanger support member 25 installed above the load-side relay unit F.
  • the load-side relay unit F which is a feature of the present embodiment, will be described in detail.
  • 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. Then, the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 have substantially the same shape, the area occupied in the load-side relay unit F is reduced, and the dimensions of the load-side relay unit F are reduced. .
  • the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 are configured by plate heat exchangers, and the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 themselves are downsized. .
  • the size of the load-side relay unit F is further reduced by minimizing the piping path that is arranged in the unit F and connects the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51.
  • positioning both heat exchangers in series facing the distance between piping junction parts can be shortened, and joining piping which connects both heat exchangers can be minimized. Therefore, the cost can be reduced by shortening the connecting piping.
  • the heat medium-refrigerant heat exchanger 51 is for exchanging heat between the heat medium circulating in the hot water supply load 3 and the refrigerant circulating in the hot water supply refrigeration cycle 2, and the heat medium is contained in the heat exchanger. Flowing. For safety, it is required to prevent the heat medium from leaking to the outside even when damage such as a crack occurs in the heat medium-refrigerant heat exchanger 51.
  • a drain receiver may be installed in order to discharge water condensed on the surface to the outside. In such a drain receiver, heat leaked from the heat medium-refrigerant heat exchanger 51 may be used. The entire amount of media cannot be received.
  • a drain pan 10 having a volume for receiving the volume of the heat medium-refrigerant heat exchanger 51 is installed below the heat medium-refrigerant heat exchanger 51.
  • the drain pan 10 is preferably subjected to at least one of a coating process, an antirust process, and an anticorrosion process. If such a process is performed, even when a heat medium is dripped onto the drain pan 10, it becomes possible to prevent the occurrence of rust and erosion corrosion due to the heat medium.
  • an inclination may be provided on the bottom surface of the drain pan 10.
  • the heat medium-refrigerant heat exchanger 51 When the heat medium-refrigerant heat exchanger 51 is directly installed on the drain pan 10, no gap is formed between the drain pan 10 and the heat medium-refrigerant heat exchanger 51. Therefore, when receiving an impact due to the drop of the load-side relay unit F or vibration during transportation, the impact is directly transmitted to the drain pan 10 and the drain pan 10 may be damaged. In particular, when the load-side relay unit F is transported over a long distance, the possibility of receiving an impact increases. In order to absorb such an impact, an impact absorbing member 20 is provided between the drain pan 10 and the heat medium-refrigerant heat exchanger 51.
  • the shock absorbing member 20 may be formed by bending a sheet metal as shown in FIG. 3, for example, and provided at a predetermined interval from the drain pan 10. Then, a predetermined space is created between the drain pan 10 and the impact absorbing member 20, and even when the load-side relay unit F receives an impact, the impact is not directly transmitted to the drain pan 10. In other words, the impact absorbing member 20 disperses the impact received by the load-side relay unit F and reduces the impact transmitted to the drain pan 10. As a result, even when the load-side relay unit F receives an impact, the drain pan 10 can be prevented from being damaged by the impact.
  • the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 are configured by plate heat exchangers
  • the present invention is not limited thereto.
  • the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 are replaced with a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, or a double tube heat exchanger. Or the like.
  • the shock absorbing member 20 is formed of a sheet metal has been described as an example, it is not limited thereto.
  • the impact-absorbing member 20 may be formed of a curable plastic with a raised bottom plate, other resin, or polystyrene foam.
  • the heat exchanger support member 25 installed above the load side relay unit F will be described.
  • the heat exchanger support member 25 is provided above the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51, and supports both heat exchangers from above.
  • the heat exchanger support member 25 is configured by bending four sides of a sheet metal at a substantially right angle.
  • the heat exchanger support member 25 has two protrusions (an X-axis direction misalignment prevention protrusion 26 and a Y-axis direction misalignment prevention protrusion 27) on one surface (the surface on the side in contact with the heat exchanger). Is formed.
  • the heat exchanger support member 25 has the four sides and two protrusions on the refrigerant-refrigerant heat exchanger 41 and heat medium-refrigerant heat exchanger 51 side so that the refrigerant-refrigerant heat exchanger 41 and the heat medium- Installed above the refrigerant heat exchanger 51.
  • the hot water circulating pipe 203 such as a water pipe is installed in the load side relay unit F, that is, when the hot water circulating pipe 203 is attached to the load side relay unit F, the screw is attached in the same manner as the pipe is attached to the normal unit.
  • the pipe is screwed into the load side relay unit F, and the hot water storage water circulation pipe 203 is constructed.
  • the X-axis direction misalignment preventing projection 26 and the Y-axis direction misalignment preventing projection 27 are formed on the heat exchanger support member 25, and refrigerant-refrigerant heat exchange is performed by these two projections.
  • the movement of the heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 is suppressed. That is, the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51 are locked by the X-axis direction misalignment preventing projection 26 and the Y-axis direction misalignment preventing projection 27, and are tightened at the time of screw pipe construction. There is no deviation even with torque.
  • a control box or the like in which a control board is disposed above the heat exchanger support member 25 (not on the side of the refrigerant-refrigerant heat exchanger 41 and the heat medium-refrigerant heat exchanger 51) is installed.
  • a part of the control box may be placed on the upper surface of the heat exchanger support member 25. By doing so, the strength of the heat exchanger support member 25 can be reinforced.

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  • 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)

Abstract

L'invention concerne une unité de relais côté charge qui héberge plusieurs échangeurs thermiques, et qui est conçue pour une réduction de taille et un travail de canalisation simplifié; et 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)) sont montés sur l'unité (F) de relais côté charge, ces échangeurs thermiques ayant une forme sensiblement identique, et étant disposés de manière que les surfaces de formation de joint de la conduite réfrigérante (45) reliant les échangeurs thermiques entre eux se fassent face.
PCT/JP2009/056054 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 WO2010109620A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2009/056054 WO2010109620A1 (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
JP2011505743A JP5202726B2 (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/JP2009/056054 WO2010109620A1 (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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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016166714A (ja) * 2015-03-10 2016-09-15 パナソニックＩｐマネジメント株式会社 熱生成ユニット
WO2016185689A1 (fr) * 2015-05-20 2016-11-24 パナソニックＩｐマネジメント株式会社 Système de climatisation et d'alimentation en eau chaude
JP2016223740A (ja) * 2015-06-03 2016-12-28 株式会社コロナ ヒートポンプ冷温水機
EP3124890A1 (fr) 2015-07-30 2017-02-01 Panasonic Intellectual Property Management Co., Ltd. Unité de génération de chaleur
EP3217117A1 (fr) * 2016-03-09 2017-09-13 Panasonic Intellectual Property Management Co., Ltd. Systeme d'alimentation en eau chaude/air conditionne

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0220085U (fr) * 1988-07-27 1990-02-09
JPH10267427A (ja) * 1997-03-25 1998-10-09 Mitsubishi Electric Corp 冷却装置
JPH11148730A (ja) * 1997-11-18 1999-06-02 Matsushita Electric Ind Co Ltd 積層式熱交換装置
JP2000121173A (ja) * 1998-10-21 2000-04-28 Sanyo Electric Co Ltd 冷凍装置
JP2004132647A (ja) * 2002-10-11 2004-04-30 Daikin Ind Ltd 給湯装置、空調給湯システム、及び給湯システム
JP2005538338A (ja) * 2002-09-10 2005-12-15 アルファ ラヴァル コーポレイト アクチボラゲット プレート熱交換器
JP2008267721A (ja) * 2007-04-23 2008-11-06 Mitsubishi Electric Corp 冷凍空調装置
JP2009002551A (ja) * 2007-06-20 2009-01-08 Takahashi Kogyo Kk 露受装置付コンベア式凍結装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0656616U (ja) * 1992-02-24 1994-08-05 株式会社富士通ゼネラル 空気調和機の室外側ユニット
JPH10281692A (ja) * 1997-03-31 1998-10-23 Zexel Corp 並設一体型熱交換器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0220085U (fr) * 1988-07-27 1990-02-09
JPH10267427A (ja) * 1997-03-25 1998-10-09 Mitsubishi Electric Corp 冷却装置
JPH11148730A (ja) * 1997-11-18 1999-06-02 Matsushita Electric Ind Co Ltd 積層式熱交換装置
JP2000121173A (ja) * 1998-10-21 2000-04-28 Sanyo Electric Co Ltd 冷凍装置
JP2005538338A (ja) * 2002-09-10 2005-12-15 アルファ ラヴァル コーポレイト アクチボラゲット プレート熱交換器
JP2004132647A (ja) * 2002-10-11 2004-04-30 Daikin Ind Ltd 給湯装置、空調給湯システム、及び給湯システム
JP2008267721A (ja) * 2007-04-23 2008-11-06 Mitsubishi Electric Corp 冷凍空調装置
JP2009002551A (ja) * 2007-06-20 2009-01-08 Takahashi Kogyo Kk 露受装置付コンベア式凍結装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016166714A (ja) * 2015-03-10 2016-09-15 パナソニックＩｐマネジメント株式会社 熱生成ユニット
WO2016185689A1 (fr) * 2015-05-20 2016-11-24 パナソニックＩｐマネジメント株式会社 Système de climatisation et d'alimentation en eau chaude
JP2016223740A (ja) * 2015-06-03 2016-12-28 株式会社コロナ ヒートポンプ冷温水機
EP3124890A1 (fr) 2015-07-30 2017-02-01 Panasonic Intellectual Property Management Co., Ltd. Unité de génération de chaleur
EP3217117A1 (fr) * 2016-03-09 2017-09-13 Panasonic Intellectual Property Management Co., Ltd. Systeme d'alimentation en eau chaude/air conditionne

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