WO2010109618A1

WO2010109618A1 - Load-side relay unit and compound air conditioning/hot water supply system mounting load-side relay unit thereon

Info

Publication number: WO2010109618A1
Application number: PCT/JP2009/056047
Authority: WO
Inventors: 智一川越; 宏典薮内; 純一亀山; 博文 ▲高▼下
Original assignee: 三菱電機株式会社
Priority date: 2009-03-26
Filing date: 2009-03-26
Publication date: 2010-09-30

Abstract

A load-side relay unit which houses a plurality of heat exchangers and a control box, and is designed for downsizing, easier transportation and easier maintenance; and a compound air conditioning/hot water supply system mounting the load-side relay unit thereon. The load-side relay unit (F) has mounted thereon at least two heat exchangers (a refrigerant-refrigerant heat exchanger (41), a heat carrier-refrigerant heat exchanger (51)) and a control board (25), wherein the control board (25) is divided into a plurality of function-specific boards that are arranged from the front side to the back side of the unit.

Description

Load-side relay unit and combined air conditioning and hot water supply system

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.

Conventionally, there are air-conditioning and hot-water supply complex systems that can simultaneously supply a cooling load, a heating load, and a hot water supply load. As such, “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). ).

International Publication WO2008 / 117408 (FIG. 1 etc.)

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. In such a heat pump device, 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). In many cases, 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. The control board is usually accommodated in a control box. In general, the control box is designed to be arranged in a plane in consideration of cost performance.

If it is a normal unit (for example, an indoor unit), the space for the control box is secured. However, when the control box is arranged in a plane with the load side unit as described in Patent Document 1, the height and length of the load side unit increase, and the load side unit cannot be stacked in a container, It is assumed that the load required for this will increase. In addition, since a plurality of heat exchangers (first load side heat exchanger and second load side heat exchanger) are mounted on the load side unit, a hot water supply compressor, a fan motor, and the like are also mounted. There is also a problem that internal space is greatly restricted in installing the control box.

The present invention has been made to solve the above-described problems, and accommodates a plurality of heat exchangers and a control box, and is intended to reduce size, facilitate transportation, and facilitate maintenance. It aims at providing a load side relay unit and an air-conditioning hot-water supply complex system carrying it.

A 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 and a control board are mounted, and the control board includes a plurality of parts divided for each function. The plurality of substrates are arranged from the front side to the back side of the unit.

In the combined air conditioning and hot water supply system according to the present invention, an air conditioning compressor, a flow path switching unit, an outdoor heat exchanger, an indoor heat exchanger, and an air conditioning throttle unit are connected in series and connected in series. The refrigerant-refrigerant heat exchanger and the hot water supply heat source throttle means include a first refrigerant circuit connected in parallel to the indoor heat exchanger and the air conditioning throttle means, and circulates the air-conditioning refrigerant in the first refrigerant circuit. An air conditioning refrigeration cycle, a hot water supply compressor, a heat medium-refrigerant heat exchanger, hot water supply throttle means, and a second refrigerant circuit in which the refrigerant-refrigerant heat exchanger is connected in series, A hot water supply 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 refrigerant-refrigerant heat exchanger, the hot water supply heat source throttle means, the heat medium-refrigerant heat exchanger, the hot water supply compressor, and the hot water supply throttle means are connected to the load-side relay unit. It is housed.

According to the load-side relay unit according to the present invention, since the plurality of boards divided for each function constitute the control board arranged from the front side to the back side of the unit, each board is arranged in a plane. The height can be shortened compared to the above, and the size can be reduced accordingly.

According to the combined air conditioning and hot water supply system according to the present invention, since the load-side relay unit is provided with a reduced size, it is possible to widen an empty space such as a machine room in which the load-side relay unit is arranged. Therefore, space saving can be realized. In addition, facilities can be concentrated in one place, and maintainability can be improved. Furthermore, the volume of the machine room can be reduced, and the living space other than the machine room can be increased.

It is a refrigerant circuit figure which shows the refrigerant circuit structure of the air-conditioning / hot-water supply complex system which concerns on embodiment. It is explanatory drawing for demonstrating the transport form of a load side relay unit. It is explanatory drawing for demonstrating the dimension of the control box mounted in a load side relay unit. It is a disassembled perspective view which shows the outline of the state which decomposed | disassembled the control box. It is the schematic for demonstrating the example of piping connection of the conventional unit. It is the schematic which shows the whole structure of external thread piping. It is a perspective view for demonstrating the piping connection part of a load side relay unit. It is a schematic explanatory drawing for demonstrating the usage example of a conventional system. It is explanatory drawing for demonstrating the usage example of an air conditioning hot-water supply complex system. It is explanatory drawing for demonstrating the installation example of a load side relay unit.

Explanation of symbols

1 Refrigeration cycle for air conditioning, 2 Refrigeration cycle for hot water supply, 3 Load for hot water supply, 21 Compressor for hot water supply, 22 Throttling means for hot water supply, 23 Drain pan, 25 Control box, 25 'Control box, 25a Service board, 25a' Service board, 25b high voltage section, 25b 'high voltage section, 25c heat sink section, 25c' heat sink section, 26 female thread piping, 27 strainer, 28 connection piping, 29 male thread piping, 31 water circulation pump, 32 hot water storage tank, 41 refrigerant-refrigerant Heat exchanger, 45 refrigerant piping, 51 heat medium-refrigerant heat exchanger, 61 heat medium inlet, 62 heat medium outlet, 71 outdoor unit, 72 indoor unit, 73 shower, 74 faucet, 75 hot water / floor heating, 75 Hot water storage tank, 76 boiler, 77 branch unit, 8 hot water supply unit, 79 chiller unit, 81 exhaust port, 82 water piping, 85 support base, 86 empty space, 90 machine room, 100 air conditioning hot water supply complex system, 101 air conditioning compressor, 102 four-way valve, 103 outdoor heat exchanger, 103a split heat exchanger, 104 accumulator, 105a check valve, 105b check valve, 105c check valve, 105d check valve, 106 high pressure side connection pipe, 107 low pressure side connection pipe, 108 gas-liquid separator, 109 distribution part 109a valve means, 109b valve means, 110 distributor, 110a check valve, 110b check valve, 111 internal heat exchanger, 112 first throttle device throttle means, 113 internal heat exchanger, 114 second relay device Narrowing means, 115 meeting part, 116 meeting part, 116a second meeting part, 117 Conditioning throttle means, 118 indoor heat exchanger, 119 hot water heat source throttle means, 130 connection piping, 131 connection piping, 132 connection piping, 133 connection piping, 133a connection piping, 133b connection piping, 134 connection piping, 134a connection piping, 134b Connection piping, 135 connection piping, 135a connection piping, 135b connection piping, 136 connection piping, 136a connection piping, 136b connection piping, 203 hot water circulation piping, 300 container, 313 pallet, 314 fixture, A heat source machine, B cooling room Machine, C heating indoor unit, D hot water supply heat source circuit, E relay machine, F load side relay unit, F 'unit, a connection part, b connection part, c connection part, d connection part.

Hereinafter, embodiments of the present invention will be described based on the drawings.
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. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

An air conditioning and hot water supply combined system 100 according to this embodiment includes an air conditioning refrigeration cycle 1, a hot water supply refrigeration cycle 2, and a hot water supply load 3, and includes an air conditioning refrigeration cycle 1 and a hot water supply refrigeration cycle 2. Is a refrigerant-refrigerant heat exchanger 41, and the hot water supply refrigeration cycle 2 and the hot water supply load 3 are heat medium-refrigerant heat exchangers 51, and are configured to exchange heat without mutual refrigerant or water mixing. Yes. In addition, 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. 1, in the air-conditioning refrigeration cycle 1, 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.

[Refrigeration cycle 1 for air conditioning]
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. Among these, 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. And 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.

{Heat source machine A}
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. Further, in the heat source unit A, 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. In addition, since the refrigerant circuit structure at the time of heating main operation is shown in FIG. 1, 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.

{Cooling indoor unit B and heating indoor unit C}
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, and 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.

That is, in the embodiment, a state is shown in which the air conditioner indoor unit B is determined to be in charge of the cooling load and the heating indoor unit C is determined to be in charge of the heating load by the relay device E. A blower such as a fan for supplying air to the indoor heat exchanger 118 may be provided in the vicinity of the indoor heat exchanger 118. For convenience, the connection pipe connected from the relay E to the indoor heat exchanger 118 is referred to as a connection pipe 133, and the connection pipe connected from the relay E to the air conditioning throttle means 117 is referred to as a connection pipe 134. Shall be explained.

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.

{Circuit D for hot water supply heat source}
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. For convenience, 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.

{Repeater E}
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.

In the first distribution unit 109, the 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. Further, in the first distribution unit 109, 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).

In the second distribution unit 110, the 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. In the second distribution unit 110, 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. To the low-pressure side connection pipe 107.

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. As with the first relay unit throttle unit 112, 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.

As described above, 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. For example, 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. Further, the type of refrigerant circulating in the air-conditioning refrigeration cycle 1 is not particularly limited. For example, natural refrigerants such as carbon dioxide (CO ₂ ), hydrocarbons, and helium, and alternatives that do not contain chlorine such as HFC410A, HFC407C, and HFC404A Either a refrigerant or a fluorocarbon refrigerant such as R22 or R134a used in existing products may be used.

Here, the heating main operation of the air-conditioning refrigeration cycle 1 will be described.
First, 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. Here, 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. On the other hand, 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.

Then, the air-conditioning refrigerant used for air-conditioning (flowing into the heating indoor unit C or the hot water supply heat source circuit D through the first repeater throttle means 112 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. Here, 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. It merges with the air conditioning refrigerant that has flowed out of the machine B. 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.

[Refrigeration cycle 2 for hot water supply]
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. For example, 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. For example, 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.

Here, the operation of the hot water supply refrigeration cycle 2 will be described.
First, 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. In 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.

[Load 3 for hot water supply]
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. For example, the water circulation pump 31 is of a type whose rotational speed is controlled by an inverter. Configure. As described above, 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.

First, 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.

Note that, as described above, 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). 2 refrigerant circuits), 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.

In addition, when a refrigerant having a low critical temperature is 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. . However, generally, when the refrigerant in the heat dissipation process is in a supercritical state, 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. The On the other hand, in general, 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.

Furthermore, considering that the recommended temperature of water stored in the hot water storage tank 32 for suppressing the growth of Legionella bacteria and the like is 60 ° C. or higher, it is assumed that the target temperature of hot water supply is often 60 ° C. or higher at a minimum. Is done. Based on the above, 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. When 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.

Moreover, although the case where the surplus refrigerant | coolant was stored by the liquid receiver (accumulator 104) in the refrigerating cycle 1 for an air conditioning was shown, it is not restricted to this, It should be stored with the heat exchanger used as a heat radiator in a refrigerating cycle. If so, the accumulator 104 may be removed. Further, 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 | capacitance of each indoor unit which comprises the refrigerating cycle 1 for an air conditioning may be made all the same, and you may make it differ from large to small.

As described above, in the combined air conditioning and hot water supply system 100 according to this embodiment, 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 the hot heat that had been discharged into the atmosphere and reuse it. Therefore, the system COP is greatly improved and energy is saved.

[Load side relay unit F]
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 explanatory diagram for explaining the transport mode of the load-side relay unit F. Based on FIG. 2, the transport mode of the load-side relay unit F will be described in comparison with the transport mode of the conventional unit. 2A shows a state in which a conventional unit (hereinafter referred to as unit F ′) is stored in the container 300, and FIG. 2B shows a state in which the load-side relay unit F is stored in the container 300. . As shown in FIG. 2, the load-side relay unit F is also stored in the container 300 and transported in the same manner as the unit F ′.

As the container 300, a dry container having a type such as a 20-foot container or a 40-foot container is generally used. The internal dimensions of the 20-foot container are about 5.93m long, about 2.35m high, and about 2.38m deep. The inner dimensions of the 40 foot container are approximately twice the length of the 20 foot container. FIG. 2 shows an example in which a 20-foot container is used as the container 300. A predetermined number of units F ′ are collectively placed on the container 300 on the pallet 313, and the side surfaces of the units F are fixed with a fixing tool 314 so as not to fall down during transportation.

The dimensions of the unit F ′ are generally about 0.70 m in length, about 1.04 m in height, and about 0.32 m in depth. Accordingly, when the pallet 313 (height 0.15 m) is inserted, the height becomes about 1.19 m. If two stages are stacked, the height is 2.38 m, which exceeds the inner height of the container 300. That is, at present, the unit F ′ can physically transport only one stack. As a result, the space above the unit F ′ stored in the container 300 is wasted, and the cost performance required for transportation is reduced.

In contrast, the load-side relay unit F has a height of about 0.85 m. Therefore, the load-side relay unit F can be made lower by about 0.19 m than the unit F ′, and the height including the pallet 313 is about 1.00 m. Even if two layers are stacked, the total height is about 2.00 m, which is within the inner height of the container 300. In other words, the load-side relay unit F can be stacked in two stages, and can transport a large number of units (for example, double the unit F ′) at a time. Since many units can be transported at once, the cost required for transportation can be reduced. The reason why the load-side relay unit F has a height of about 0.85 m will be described below.

FIG. 3 is an explanatory diagram for explaining the dimensions of the control box 25 mounted in the load-side relay unit F. FIG. 4 is an exploded perspective view showing an outline of a state in which the control board accommodated in the control box 25 is disassembled. Based on FIGS. 3 and 4, the reason why the height of the load-side relay unit F can be about 0.85 m will be described in comparison with the unit F ′. FIG. 3A shows the dimensions of the unit F ′, and FIG. 3B shows the dimensions of the load-side relay unit F. As shown in FIG. 3A, a control box 25 'is provided in the upper part and a drain pan 23 is provided in the lower part in the unit F'.

On the other hand, in the load side relay unit F, although the control box 25 is provided in the upper part, the drain pan is not provided in the lower part. By doing so, the load-side relay unit F can delete the drain pan height (0.07 m). In the load-side relay unit F, the length and height of the control box 25 are shorter than the length and height of the control box 25 '. By doing so, the load-side relay unit F can delete the length (0.32 m) and height (0.12 m) of the control box 25.

The control board accommodated in the control box 25 is usually a service board 25a on which a control circuit or the like is mounted, a high voltage part 25b (high voltage part board), and a heat sink part 25c in which an air path part is combined. (Heat sink part substrate). Similarly, the control box 25 'accommodates a control board composed of a service board 25a', a high voltage part 25b ', and a heat sink part 25c'. In the control box 25 ′, the service board 25 a ′, the high voltage part 25 b ′, and the heat sink part 25 c ′ are arranged in a plane. On the other hand, in the control box 25, the service board 25a, the high voltage part 25b, and the heat sink part 25c are arranged sequentially from the left side of the drawing.

By doing so, the length (0.41 m) and height (0.43 m) of the control box 25 are made shorter than the length (0.73 m) and height (0.55 m) of the control box 25 ′. It is possible. That is, in the load side relay unit F, it is possible to delete the length (0.32 m) and height (0.12 m) of the control box 25. As described above, the load-side relay unit F can be lower than the unit F ′ by the height of the drain pan (0.07 m) and the height of the control box 25 (0.12 m). Therefore, as described in FIG. 2, the load-side relay unit F is 0.19 m lower than the height of the unit F ′.

In addition, the control box 25 is installed so that the service board 25a is on the front side of the load-side relay unit F. Therefore, the maintenance of the service board 25a can be performed only by opening the cover (not shown) provided on the front side of the load-side relay unit F, and the ease of maintenance can be realized. Moreover, since the high voltage part 25b will be installed in the back back side of the service board 25a, it becomes possible to reduce the danger to an operator at the time of a maintenance.

FIG. 5 is a schematic diagram for explaining an example of pipe connection of the unit F ′. FIG. 6 is a schematic diagram showing the overall configuration of the male screw pipe 29. FIG. 7 is a perspective view for explaining a pipe connection portion of the load side relay unit F. FIG. A pipe connection to the load-side relay unit F will be described with reference to FIGS. The unit F ′ is equipped with a heat medium-refrigerant heat exchanger (same as the heat medium-refrigerant heat exchanger 51), and the hot water circulation pipe for conducting the heat medium (same as the hot water circulation pipe 203). ) Is connected.

As shown in FIG. 5, the unit F ′ is connected to the inlet side of the heat medium for the purpose of protecting the heat medium-refrigerant heat exchanger (for example, protecting the heat medium flow path from being blocked by dust). Generally, a strainer 27 is installed in the female screw pipe 26 via a connection pipe 28. As described above, it is common to use the female screw pipe 26 for the connection portion of the unit F ′ and the connection pipe 28 for the connection of the strainer 27.

In the load-side relay unit F according to this embodiment, the strainer 27 is directly connected to the male screw pipe 29 by connecting the male screw pipe 29 as shown in FIG. 5 to the inlet side of the heat medium. . By doing so, the connection pipe 28 is not necessary, and the pipe connection portion on the inlet side of the heat medium can be simplified. In addition, since the number of pipe connection points is reduced, it is possible to efficiently suppress heat medium leakage from the pipe connection portion. Furthermore, by attaching the strainer 27 to the male screw pipe 29 connected to the inlet side of the heat medium, it is possible to prevent clogging of dust and the like, and it is possible to improve the reliability and extend the life.

In the load-side relay unit F, a heat medium inlet side opening (heat medium inlet 61) and a heat medium outlet side opening (heat medium outlet 62) are provided in the lower part. By doing so, the heat medium piping (pipe 203 for circulating hot water) can be consolidated, and the piping design before construction is easy to decide. Also, by consolidating the hot water circulation pipe 203 at the lower part of the load-side relay unit F, the pipe can be shortened compared to the structure having the heat medium inlet 61 and the heat medium outlet 62 above and below the unit. The piping material is reduced, and the cost can be reduced accordingly.

From here, the usage example of the air-conditioning hot-water supply complex system 100 is demonstrated.
FIG. 8 is a schematic explanatory diagram for explaining an example of use of a conventional system. Based on FIG. 8, while describing the specific usage example of the conventional system, the usage example of the air-conditioning and hot water supply complex system 100 will be described. FIG. 8A shows an example of a conventional system in which the air conditioning equipment and the hot water supply equipment are separated, and FIG. 8B shows a separate chiller unit 79 in which the air conditioning equipment and the hot water supply equipment are integrated. Examples of conventional systems are shown respectively.

In the conventional system as shown in FIG. 8 (a), an air conditioner composed of an outdoor unit 71 and an indoor unit 72, a boiler 76 for boiling water, a hot water storage tank 75, a shower 73, a faucet 74, and hot water / floor. A hot water supply facility constituted by the heating 75 is separated. In such a system, for example, in a building having a plurality of rooms such as a hotel, an apartment, a condominium, and a building, the air conditioning equipment and the hot water supply equipment must be provided separately, which increases the labor and cost required for installation. In addition, the installation space of the heat source machine (the outdoor unit 71 and the boiler 76) must be taken into consideration.

In the conventional system as shown in FIG. 8B, although the air conditioning equipment and the hot water supply equipment are integrated, the indoor unit 72, the hot water supply unit 78, and the chiller unit necessary for cooling are provided via the branch unit 77. 79 is connected. In such a system, it is not necessary to separately provide air conditioning equipment and hot water supply equipment, but for each hot water supply equipment (equipment comprising hot water storage tank 75, shower 73 and faucet 74, and equipment comprising hot water / floor heating 75). The hot water supply unit 78 and the chiller unit 79 must be provided separately, which requires a lot of labor and cost for installation, and the installation space for these units must be taken into consideration.

In contrast, in the air conditioning and hot water supply complex system 100, by providing the load-side relay unit F, the air conditioning facility and the hot water supply facility can be integrated without providing a chiller unit (described in detail with reference to FIG. 9). ). For example, when hot water is supplied to a pool or a large bathing facility provided in a leisure facility, it is necessary to separately provide a boiler 76 and a chiller unit 79 in the conventional system. 79 need not be provided separately. Therefore, devices such as the boiler 76 and the chiller unit 79 can be reduced. Moreover, it is not necessary to consider the installation space.

FIG. 9 is an explanatory diagram for explaining an example of use of the air conditioning and hot water supply complex system 100. Based on FIG. 9, the specific usage example of the air-conditioning hot-water supply complex system 100 is demonstrated in detail. FIG. 9A shows a usage example of the conventional system, FIG. 9B shows a usage example of the air conditioning and hot water supply complex system 100, and FIG. 9C shows another usage example of the air conditioning and hot water supply complex system 100. Yes. FIG. 9A shows an example of use when the boiler 76 constituting the conventional system described in FIG. 8 is installed.

9A, the boiler 76 and the hot water storage tank 75 are provided in the machine room 90. A hot water storage tank 75 connected to the boiler 76 by a water pipe 82 (conceived by the hot water storage water circulation pipe 203 of the air conditioning and hot water supply complex system 100) is provided. Further, the boiler 76 is provided with an exhaust port 81. Then, in the conventional system, since the heat source is provided together with the boiler 76, the empty space 86 is narrowed.

In FIG. 9B, the machine room 90 includes a load-side relay unit F and a hot water storage tank 32 that function as a hot water supply unit. A hot water storage tank 32 connected by a hot water circulation pipe 203 is provided in the vicinity of the load-side relay unit F. Then, since the load-side relay unit F is not provided with the heat source unit A, the load side relay unit F is smaller than the boiler 76 of the conventional system. Therefore, the empty space 86 in the machine room 90 is widened.

In FIG. 9 (c), the machine room 90 includes a wall-mounted load-side relay unit F that functions as a hot water supply unit and a hot water storage tank 32. A hot water storage tank 32 connected by a hot water circulation pipe 203 is provided below the load-side relay unit F. As a result, the load-side relay unit F is not provided with the heat source unit A, and is used for hanging on the wall using the upper space of the machine room 90, so that the empty space 86 in the machine room 90 is further widened. The load-side relay unit F is supported by a support base 85 fixed to the wall surface of the machine room 90.

According to the comparison of FIG. 9, the use of the load-side relay unit F makes the empty space 86 wide, and space saving can be realized. By realizing space saving, facilities can be concentrated in one place, and maintainability can be improved. Further, by realizing space saving, the volume of the machine room 90 can be reduced, and the living space other than the machine room 90 can be increased. Furthermore, since it can be installed even if the machine room 90 is small, it can also be installed in places where it is difficult to introduce the boiler 76 and the chiller unit 79. Since equipment such as the boiler 76 and the chiller unit 79 can be reduced, the process, time and cost required for construction can be reduced. Material costs for construction (for example, for piping materials) can also be reduced.

FIG. 10 is an explanatory diagram for explaining an installation example of the load-side relay unit F. Based on FIG. 10, the state which installed the several load side relay unit F and the several hot water storage tank 32 in the machine room 90 is demonstrated. 10A shows a state where the load-side relay unit F is placed horizontally in the machine room 90, and FIG. 10B shows a state where the load-side relay unit F is stacked and installed in the machine room 90. Yes. As shown in FIG. 1, a plurality of load-side relay units F can be connected via a relay E. That is, as shown in FIG. 10, a case where a plurality of load-side relay units F are installed is assumed.

When installing a plurality of hot water storage tanks 32 in the machine room 90, a plurality of load-side relay units F are also installed according to the number of hot water storage tanks 32. As described above, the load-side relay unit F itself is downsized. However, if a plurality of load-side relay units F are installed in the machine room 90, that much space is required (see FIG. 10A). Thus, by stacking the load-side relay units F, the space in the machine room 90 can be saved.

As described above, in the air conditioning and hot water supply complex system 100, the load-side relay unit F is downsized, so that the cost required for transportation can be reduced (see FIG. 2). In this air conditioning and hot water supply complex system 100, the control box 25 is improved, so that maintenance and safety can be improved (see FIG. 4). In this air conditioning and hot water supply complex system 100, the piping connection portion of the load-side relay unit F can be simplified, so that leakage of the heat medium from the piping connection portion can be suppressed (see FIG. 6). In this air conditioning and hot water supply complex system 100, since the strainer 27 can be attached to the male screw pipe 29 connected to the load-side relay unit F, the reliability can be improved and the life can be extended (see FIG. 6).

In this air-conditioning and hot water supply complex system 100, the hot water storage water circulation pipes 203 connected to the load-side relay unit F can be consolidated, so that it is easy to determine the piping design before construction, and the hot water hot water circulation pipes 203 can be shortened (see FIG. 7). In this air conditioning and hot water supply complex system 100, space saving of the machine room 90 in which the load-side relay unit F is installed can be realized, so that the facilities can be concentrated in one place and the maintainability can be improved. In this air conditioning and hot water supply complex system 100, the volume of the machine room 90 can be reduced, so that the living space other than the machine room 90 can be increased (see FIG. 9).

Boiler hot water supply heat source (e.g., boiler 76 of conventional systems) is used combustion system, such as, many boilers, by creating a high-temperature heat source by burning fossil fuels, increased CO ₂ emissions are concerned The On the other hand, in the air conditioning and hot water supply complex system 100, electricity is mainly used as an operating source, so that CO ₂ emission can be greatly reduced. According to a survey by the Japan Atomic Energy Culture Foundation, it is known that CO ₂ emissions are 53% in the air conditioning and hot water supply complex system 100.

In the case of the combustion method, exhaust (for the exhaust port 81 shown in FIG. 9A) for discharging the gas generated by combustion to the atmosphere is necessary, whereas in the case of the air conditioning and hot water supply complex system 100, gas is generated. Therefore, there is no need to install intake / exhaust equipment, and installation and construction costs can be reduced. In the case of the combustion system, the efficiency of the amount of heat obtained with respect to the input energy is poor, whereas in the case of the air conditioning and hot water supply combined system 100, since the heat pump system is used, it is possible to extract more heat than the input energy.

Even for electric heaters that use the same electricity as the operating source, the amount of heat obtained with respect to power consumption is large and efficient, so the cost can be kept low. Moreover, since it is necessary for the electric heater to periodically replace the electric heating coil, it takes a lot of labor and cost for maintenance. In contrast, in the air-conditioning and hot water supply complex system 100, even if maintenance is performed periodically, the amount of heat obtained for power consumption is large, and the running cost can be reduced.

In the air conditioning and hot water supply complex system 100, since air conditioning systems such as a boiler system and a chiller system can be integrated into the same system, monitoring and maintenance work of the system can be facilitated. In addition, although demonstrated as leisure facilities in FIG. 8, it is not limited to it, For example, a restaurant, a department store, a gym, a hospital, etc. can acquire the same effect. In addition, in facilities that handle foods such as restaurants and grocery stores, if the air conditioning hot water supply complex system 100 is configured to be able to exchange heat with a low temperature equipment system, it can be used alone or in combination with outdoor air conditioning or water. The heat source machine can also be frozen.

When the heat source of the air conditioning and hot water supply complex system 100 is transferred by a water heat source machine, heat can be stored if the obtained water heat source is stored. Moreover, when exchanging the heat source of the air-conditioning / hot-water supply combined system 100 by outdoor air-conditioning, if the obtained hot water is periodically supplied to the heat exchanger in winter, the operation stop due to the defrosting operation can be suppressed. Furthermore, in areas where there is snow, hot water obtained by the air conditioning and hot water supply complex system 100 can be used for snow removal.

Although the object of heat transfer to the hot water supply is water, a solution in which other substances are dissolved in water or a medium other than water may be used. For example, it may be a milk drink such as milk instead of water. When a milk beverage is used as a heat medium, it can be used as a high temperature sterilization facility. Moreover, although the case where the outdoor heat exchanger 103 mounted on the heat source unit A performs heat exchange between air and refrigerant has been described as an example, the heat source is not limited to air, but water, antifreeze liquid (brine, etc.), geothermal heat, etc. Other heat sources may be used. If necessary, it may be used in combination with other heat source methods.

Claims

A load-side relay unit of a refrigeration cycle apparatus in which at least two heat exchangers and a control board are mounted,
The control board includes a plurality of boards divided for each function,
The plurality of substrates are arranged from the front side to the back side of the unit.
The control board is
The load-side relay unit according to claim 1, wherein the load-side relay unit is housed in a control box.
The control board is
It consists of a service board on which the control circuit is mounted, a high voltage part board, and a heat sink part board,
The load-side relay unit according to claim 1 or 2, wherein the service board is arranged on the front side and the heat sink unit board is arranged on the back side.
At least one of the heat exchangers is a heat medium-refrigerant heat exchanger that executes a heat exchanger between a heat medium and a refrigerant different from the heat medium.
The load-side relay unit according to any one of claims 1 to 3, wherein a male screw pipe is connected to an inlet side of a heat medium flowing into the heat medium-refrigerant heat exchanger.
The load-side relay unit according to claim 4, wherein a strainer is directly connected to the male screw pipe.
5. The heat medium inlet flowing into the heat medium-refrigerant heat exchanger and the heat medium outlet flowing out of the heat medium-refrigerant heat exchanger are both provided below. 5. The load side relay unit according to 5.
The compressor for air conditioning, the flow path switching means, the outdoor heat exchanger, the indoor heat exchanger, and the throttle means for air conditioning are connected in series, and for the refrigerant-refrigerant heat exchanger and hot water supply heat source connected in series. An air-conditioning refrigeration cycle, wherein the throttle means comprises 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;
A hot water supply compressor, a heat medium-refrigerant heat exchanger, hot water supply throttling means, and a second refrigerant circuit in which the refrigerant-refrigerant heat exchanger is connected in series, and the second refrigerant circuit has a hot water supply refrigerant Refrigeration cycle for hot water supply that circulates
A water circulation pump, a water circuit in which the heat medium-refrigerant heat exchanger, and a hot water storage tank are connected in series, and a hot water supply load for circulating hot water in the water circuit,
The refrigerant-refrigerant heat exchanger, the hot water supply heat source throttle means, the heat medium-refrigerant heat exchanger, the hot water supply compressor, and the hot water supply throttle means are any one of the first to sixth aspects. It is housed in the load side relay unit described in 1.
The load-side heat exchanger is
It is installed on a floor surface or a wall surface. The air conditioning and hot water supply combined system according to claim 7.
In connecting a plurality of the load side heat exchangers,
The air-conditioning and hot-water supply complex system according to claim 7, wherein the load-side relay units are arranged side by side or stacked.