JP2018063093A - Heat pump water heater with heating function - Google Patents

Abstract

PROBLEM TO BE SOLVED: To optimally control flow division balance of a refrigerant divided into a water-refrigerant heat exchanger side and an indoor heat exchanger side in a boiling-up/heating operation.SOLUTION: In a boiling-up/heating operation, an opening of an expansion valve 111 disposed in a pipe conduit at a water-refrigerant heat exchanger 15 side and an opening of an expansion valve 112 disposed in a pipe conduit at an indoor heat exchanger 27 side are variably controlled according to boiling-up requested capacity and heating requested capacity, and flow division balance to both pipe conduits is controlled. Further an opening of an expansion valve 113 disposed at a downstream side with respect to a joining point E where a refrigerant at the water-refrigerant heat exchanger 15 side and a refrigerant at the indoor heat exchanger 27 side are joined, is feedback controlled by an expansion valve control portion 410C so that a refrigerant discharge temperature Tout is kept at a prescribed fixed value. Thus the flow division balance of the water-refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side is optimally controlled while keeping a high boiling-up temperature Tb, and an operation can be stably continued.SELECTED DRAWING: Figure 13

Description

  The present invention relates to a heat pump water heater with a heating function capable of performing boiling and heating operations in which heating of indoor air and heating of hot water in a hot water storage tank are performed in parallel.

  Conventionally, in this type of water heater, as described in Patent Document 1, a water refrigerant heat exchanger and an indoor heat exchanger are respectively arranged in two pipes branched and connected from the discharge side of the compressor, and compressed. The refrigerant discharged from the machine is led to a water-refrigerant heat exchanger and an indoor heat exchanger to condense, so that hot water in the hot water storage tank and indoor air are heated together (= boiling / heating operation). It was.

JP 2009-92321 A

  When performing the boiling / heating operation, the refrigerant from the compressor is divided into the water refrigerant heat exchanger side pipe and the indoor heat exchanger side pipe as described above. It needs to be controlled in some way. However, the above-described conventional technique has a problem that no particular consideration is given to the control of such a diversion balance.

  In order to solve the above-described problems, in claim 1 of the present invention, an indoor heat exchanger as a condenser that performs heat exchange between the refrigerant and room air, a hot water storage tank that stores hot water, a refrigerant passage, and a water passage. A water refrigerant heat exchanger as a condenser that exchanges heat between the refrigerant in the refrigerant passage and water in the water passage, and an evaporator that exchanges heat between the refrigerant and outside air. A heat pump heat exchanger and a compressor, the water passage of the water-refrigerant heat exchanger and the hot water storage tank are annularly connected by hot water piping to form a hot water circulation circuit, and the indoor heat exchanger A refrigerant circulation circuit is formed by connecting the refrigerant passage of the water refrigerant heat exchanger, the heat pump heat exchanger, and the compressor with refrigerant piping, and heats indoor air by the indoor heat exchanger; To the hot water storage tank by the water refrigerant heat exchanger In the heat pump water heater with a heating function capable of performing boiling and heating operation for heating the refrigerant pipe, the refrigerant pipe is connected to a discharge side of the compressor, and a predetermined amount with respect to the discharge side pipe A first branch line branched from the branch point and connected with the water-refrigerant heat exchanger, and connected to the discharge side pipe branched from the branch point, and the indoor heat exchanger is arranged. The heat pump heat is defined as a junction where the second pipe, the first pipe downstream from the water-refrigerant heat exchanger, and the second pipe downstream from the indoor heat exchanger merge. A third pipe connected to the inlet side of the exchanger; and a suction side pipe connecting the outlet side of the heat pump heat exchanger to the suction side of the compressor, wherein the first pipe The second conduit includes a second decompressor, and the third conduit includes a second decompressor. The refrigerant having a pressure reducer, adjusting the valve openings of the first pressure reducer and the second pressure reducer, and separately flowing from the discharge side pipe to the first pipe and the second pipe And a discharge temperature control means for adjusting the valve opening of the third pressure reducer and controlling the refrigerant discharge temperature of the refrigerant discharged from the discharge side of the compressor. It is a thing.

  Further, in the present invention, the shunt control means includes a required heat exchange capability in the indoor heat exchanger and a required heat exchange capability in the water refrigerant heat exchanger while fixing the valve opening of the first pressure reducer. Accordingly, the flow rate of the second pressure reducer is variably controlled to control the diversion ratio between the first pipeline side and the second pipeline side.

  According to a third aspect of the present invention, the shunt control means includes the first pressure reducer and the first pressure reducer according to a first required heat exchange capability of the water refrigerant heat exchanger and a second required heat exchange capability of the indoor heat exchanger. The diversion ratio between the first pipeline side and the second pipeline side is controlled by variably controlling the valve opening degree of the second decompressor.

  According to the first aspect of the present invention, the refrigerant circuit is formed by connecting the heat pump heat exchanger, the compressor, the water refrigerant heat exchanger, and the indoor heat exchanger with the refrigerant pipe. In the refrigerant pipe, the first pipe and the second pipe are connected to the discharge side pipe connected to the discharge side of the compressor while being branched from each other (from a predetermined branch point). The first pipe is provided with a water-refrigerant heat exchanger, the second pipe is provided with an indoor heat exchanger, and the downstream side of the first and second pipes has a predetermined junction point. In each other). The junction is connected to the outdoor heat exchanger by a third pipe, and the outdoor heat exchanger is connected to the suction side of the compressor by a suction side pipe.

  Thereby, the compressor → the suction side pipe → the branch point, the branch point → the first pipe (water refrigerant heat exchanger) → the junction, and the branch → the second pipe (indoor heat exchanger) → the junction. Furthermore, the path of junction point → third pipe → heat pump heat exchanger → suction side pipe → compressor can be realized. As a result, part of the high-temperature and high-pressure refrigerant gas discharged from the compressor dissipates heat to the indoor air in the indoor heat exchanger and condenses into a liquid refrigerant, while the remaining high-temperature and high-pressure refrigerant gas discharged from the compressor In the water-refrigerant heat exchanger, heat is transferred to the hot water pipe that leads to the hot water storage tank, where it condenses into liquid refrigerant.Then, the liquid refrigerant evaporates in the heat pump heat exchanger, and then absorbs heat from the outside air and returns to the compressor. The indoor air and the hot water in the hot water storage tank can be heated (= boiling / heating operation).

  At this time, since the refrigerant from the compressor is divided into the first pipe and the second pipe as described above, it is necessary to control the flow balance in some form. According to claim 1, a first decompressor is provided in the first pipeline to the water-refrigerant heat exchanger among the branched first pipeline and the second pipeline, and the indoor heat exchanger is provided. A second pressure reducer is provided in the second pipe line. However, if the control of the diversion balance is performed only by the first pressure reducer of the first pipe and the second pressure reducer of the second pipe, the change in the refrigeration cycle of the refrigerant path is large, and the compression is reduced. The refrigerant discharge temperature from the machine is not stable. For example, when the refrigerant discharge temperature is too low, the amount of heat exchange in the water / refrigerant heat exchanger is reduced, the boiling temperature in the hot water pipe is lowered, and so-called hot water shortage may occur in the hot water storage tank. In addition, when the refrigerant discharge temperature is too high, the operation may be stopped by the circuit protection function.

  Therefore, according to the first aspect, the third pressure reducer is provided in the third pipeline downstream of the junction. The diversion control unit controls the valve openings of the first pressure reducer and the second pressure reducer to control the flow of refrigerant, while the discharge temperature control unit controls the valve opening of the third pressure reducer. By doing so, the refrigerant discharge temperature is controlled. This makes it possible to keep the refrigerant discharge temperature constant unlike the case where the control of the diversion balance is performed only by the first decompressor and the second decompressor. As a result, it is possible to optimally control the diversion balance while maintaining a high boiling temperature and to continue the operation stably.

  According to the second aspect of the invention, the valve opening degree of the second pressure reducer on the indoor heat exchanger side is made variable while the valve opening degree of the first pressure reducer on the water refrigerant heat exchanger side is fixed. Control the ratio. Thereby, a diversion ratio can be changed quickly with a simple control mode.

  According to the third aspect of the present invention, the diversion ratio is controlled by making the valve openings of both the first pressure reducer on the water refrigerant heat exchanger side and the second pressure reducer on the indoor heat exchanger side variable. Thereby, a diversion ratio can be changed with high accuracy.

1 is an external configuration diagram of a main unit of a heat pump water heater with a heating function according to an embodiment of the present invention. Circuit diagram of the entire heat pump water heater Functional configuration diagram of heat-pump control unit Functional configuration diagram of hot water storage control unit Functional configuration diagram of air conditioner control unit Diagram explaining operation during boiling operation The figure showing the control aspect of the compressor rotation speed at the time of boiling operation, heating operation, and both boiling and heating operations The figure explaining the action at the time of cooling operation Diagram explaining operation during boiling / cooling operation The figure explaining the action at the time of heating operation Diagram explaining operation during boiling and heating operation The figure showing the control map when an expansion valve control part performs the opening degree control of each expansion valve The figure explaining the stability effect of discharge temperature in comparison with a comparative example The figure showing the control map when an expansion valve control part performs the opening degree control of each expansion valve in the modification which fixes the opening degree of one expansion valve, and makes the opening degree variable only the other expansion valve. The figure explaining the modification which replaced the two-way valve with the expansion valve by the pipe line by the side of a water refrigerant heat exchanger

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 shows an external configuration of a main unit of a heat pump water heater 1 with a heating function (but also with a cooling function) according to the present embodiment. In FIG. 1, a heat pump water heater 1 of this embodiment includes a hot water storage unit 100 provided with a hot water storage tank 2 (see FIG. 2 and the like described later), a heat pump unit 300 as an outdoor unit, and an air conditioner unit 200 as an indoor unit. have.

  FIG. 2 shows a circuit configuration of the entire heat pump water heater 1 of the present embodiment. As shown in FIG. 2, the hot water storage unit 100 includes a refrigerant-side flow path 15 b and a water-side flow path 15 a for circulating the refrigerant, and exchanges heat between the high-temperature and high-pressure refrigerant and the hot water in the hot water storage tank 2. A water refrigerant heat exchanger 15 that functions as a condenser that performs heating, and a boiling pump 19. That is, the water-side flow path 15a of the water-refrigerant heat exchanger 15 and the hot water storage tank 2 are annularly connected by a heating forward pipe 5 and a heating return pipe 6 serving as hot water piping, and hot water is stored in the hot water storage unit 100. A heating circulation circuit 4 as a circulation circuit is formed.

  The heating forward pipe 5 is connected to the lower part of the hot water storage tank 2, and the heating return pipe 6 is connected to the upper part of the hot water storage tank 2. The boiling pump 19 is provided in the middle of the heating forward pipe 5, and the hot water from the heating forward pipe 5 is circulated to the heating return pipe 6 through the water-side flow path 15a while Circulate hot water. The heating forward pipe 5 is provided with an incoming water temperature sensor 23 for detecting an incoming water temperature T1 (hot water inlet temperature) flowing into the water-side flow path 15a of the water-refrigerant heat exchanger 15. The return pipe 6 is provided with a boiling temperature sensor 24 for detecting a boiling temperature Tb flowing out from the water-side flow path 15a toward the hot water storage tank 2.

  A plurality of hot water storage temperature sensors 12 for detecting the temperature of hot water in the hot water storage tank 2 (hot water storage temperature) and detecting the heating status of the hot water (in other words, the status of hot water storage) are provided on the side surface of the hot water storage tank 2. ing. A water supply pipe 7 for supplying water to the hot water storage tank 2 is connected to the lower part of the hot water storage tank 2, and a hot water discharge pipe 8 for discharging hot water stored therein is also connected to the upper part of the hot water storage tank 2. A water supply bypass pipe 9 is branched from the water supply pipe 7. Furthermore, a mixing valve 10 that mixes the hot water from the tap water pipe 8 and the water from the water supply bypass pipe 9 into hot water at a hot water supply set temperature, and a hot water temperature sensor 11 that detects the hot water temperature after mixing by the mixing valve 10; , Is provided.

  On the other hand, the refrigerant circulation circuit 30 capable of heating hot water in the hot water storage tank 2 by heat exchange (details will be described later) in the water refrigerant heat exchanger 15 includes the heat pump unit 300, the hot water storage unit 100, and the air conditioner unit 200. It is provided over. The refrigerant circuit 30 includes a heat pump circuit unit 30A disposed in the heat pump unit 300, a hot water storage circuit unit 30B disposed in the hot water storage unit 100, and an air conditioner circuit unit 30C disposed in the air conditioner unit 200. Including.

  The heat-pump circuit unit 30A includes a refrigerant pipe 18 serving as a flow path for the refrigerant, and a condenser or an evaporator by heat exchange between the compressor 14 that compresses the refrigerant, a four-way valve 31, and the refrigerant and outside air. And an outdoor heat exchanger 17 as a heat pump heat exchanger that selectively functions (details will be described later) are connected by the refrigerant pipe 18. The outdoor heat exchanger 17 is provided with an outdoor fan 67 for passing outside air through the outdoor heat exchanger 17.

  Specifically, the refrigerant pipe 18 is connected to the pipe section 18a via the pipe section 18a on the discharge side of the compressor 14 and the four-way valve 31 during the boiling operation (see FIG. 6 described later). And a piping part 18b. The pipe portion 18 b communicates with a communication conduit 101 that connects the heat pump unit 300 and the hot water storage unit 100 at a connection port 68 a that is an outlet to the outside of the heat pump unit 300.

  The refrigerant pipe 18 is connected to the pipe portion 18c on the suction side of the compressor 14 and the compressor 14 side (in other words, the boiling point) of the outdoor heat exchanger 17 during a boiling operation (see FIG. 6 described later). The outlet side during the upper operation, etc. The same applies hereinafter (see FIG. 6 and the like to be described later) and the piping part 18d for connecting to the piping part 18c via the four-way valve 31, and the anti-compressor 14 side of the outdoor heat exchanger 17 ( In other words, it includes a piping portion 18e connected to the inlet side during the above-mentioned boiling operation, etc., and so on (see FIG. 6 and the like described later). The pipe portion 18e includes an expansion valve 113 as a third pressure reducer, and is connected to a communication pipe line 102 that connects the heat pump unit 300 and the hot water storage unit 100 at a connection port 68b different from the connection port 68a. Communicate.

  The four-way valve 31 is a valve having four ports, and the remaining pipe portions are respectively connected to the two ports for the pipe portions 18b and 18d (which constitute the refrigerant main path) in the refrigerant pipe 18. Which of the two ports for 18a and 18c is connected is switched. The two ports for the pipe portions 18a and 18c are connected to each other by a refrigerant sub route including the pipe portions 18a and 18c arranged in a loop shape, and the compressor 14 is provided on the refrigerant sub route. ing. For example, when the four-way valve 31 is switched to the state shown in FIG. 6 described later (hereinafter referred to as “switching to the heating side” or the like as appropriate), the pipe portion 18a on the discharge side of the compressor 14 is connected to the water. When connected to the pipe section 18b on the inlet side of the refrigerant heat exchanger 15 and switched to the state shown in FIG. 8 (to be referred to as “switching to the cooling side” hereinafter), the pipe section 18a. Is communicated with the pipe portion 18d on the outdoor heat exchanger 17 side.

  The compressor 14, the four-way valve 31, the outdoor heat exchanger 17, the outdoor fan 67, the expansion valve 113, and the like are included in the housing of the heat pump unit 300 (see FIG. 1).

  The hot water storage circuit section 30 </ b> B includes a refrigerant pipe 25 that serves as the refrigerant flow path, and the refrigerant-side flow path 15 b of the water-refrigerant heat exchanger 15 is connected to the refrigerant pipe 25.

  Specifically, the refrigerant pipe 25 includes a pipe part 25 a communicating with the communication pipe line 101 at a connection port 75 a serving as an outlet to the outside of the hot water storage unit 100, and an end D (hereinafter simply referred to as “ A pipe portion 25b that is branched from the branch point D) and connected to the inlet side of the water-refrigerant heat exchanger 15 (specifically, the refrigerant-side flow passage 15b). And a pipe portion 25c connected to the outlet side of the water-refrigerant heat exchanger 15 (specifically, the refrigerant-side flow path 15b). The pipe part 25b includes a two-way valve 121 as a first two-way valve capable of opening and closing the pipe part 25b on the inlet side of the four-way valve 31 and the water-refrigerant heat exchanger 15, and the pipe part 25c includes an expansion valve 111 with a fully-closed function as a first pressure reducer.

  The refrigerant pipe 25, like the pipe part 25b, is connected to a pipe part 25d1 branched from the branch point D of the pipe part 25a and a pipe part connected to the anti-branch point D side of the pipe part 25d1. 25d2. The pipe portion 25d2 on the side opposite to the pipe portion 25a communicates with a communication conduit 104 that connects the hot water storage unit 100 and the air conditioner unit 200 at a connection port 95a serving as an outlet to the outside of the hot water storage unit 100.

  Further, the refrigerant pipe 25 is a pipe part that is branched and connected from an end E of the pipe part 25c on the side of the anti-water refrigerant heat exchanger 15 (hereinafter, simply referred to as “merging point E”, the merging behavior will be described later). 25e2 and a pipe part 25e1 connected to the anti-confluence point E side of the pipe part 25e2, and the anti-pipe part 25e2 side communicates with the communication pipe line 102 at a connection port 75b different from the connection port 75a; A piping portion 25f that communicates the piping portion 25d and the piping portion 25e2, and a branching connection from the junction E of the piping portion 25c as well as the piping portion 25e2, and an outlet to the outside of the hot water storage unit 100 The connection port 95b includes a piping portion 25g that communicates with the communication conduit 103 that connects the hot water storage unit 100 and the air conditioner unit 200. The piping part 25d1 includes a two-way valve 122 as a second two-way valve capable of opening and closing the piping part 25d1, and the piping part 25e2 includes a two-way valve 123 capable of opening and closing the piping part 25e2. The pipe section 25f includes a two-way valve 124 that can open and close the pipe section 25f, and the pipe section 25g includes an expansion valve 112 with a fully-closed function as a second pressure reducer. As a result, the two-way valve 123 has a function of opening and closing a pipe line between the expansion valve 113 and the expansion valve 112, and the expansion valve 111 is connected to the outlet side of the water refrigerant heat exchanger 15 and the A function of opening and closing a pipe line between the expansion valve 112 and the expansion valve 112 is provided. The communication conduit 101 has a function of communicating the two-way valves 121 and 122 and the four-way valve 31, and the communication conduit 102 connects the two-way valves 123 and 124 and the expansion valve 113. It has a function to communicate. In other words, the hot water storage unit 100 and the heat pump unit 300 are connected by the communication pipes 101 and 102 (see also FIG. 1).

  The two-way valves 121, 122, 123, 124, the expansion valves 111, 112, the water / refrigerant heat exchanger 15, the hot water storage tank 2, and the like are included in the casing of the hot water storage unit 100 (FIG. 1). reference). The expansion valve 112 may be provided in a piping part 26b described later (that is, in the casing of the air conditioner unit 200).

  The air conditioner circuit section 30C includes a refrigerant pipe 26 that serves as a flow path for the refrigerant, and indoor heat that selectively functions as a condenser or an evaporator (details will be described later) by heat exchange between the refrigerant and room air. An exchanger 27 is connected to the refrigerant pipe 26. The indoor heat exchanger 27 is provided with an indoor fan 77 (functioning as a cooling fan during cooling operation and boiling / cooling operation) for passing indoor air through the indoor heat exchanger 27.

  Specifically, the refrigerant pipe 26 communicates with the communication pipe 104 at a connection port 76 a serving as an outlet to the outside of the air conditioner unit 200, and the anti-communication pipe 104 side is the connection port 76 a of the indoor heat exchanger 27. The pipe section 26a connected to the side (in other words, the inlet side during heating operation, the same applies hereinafter, see FIG. 10, etc.) and the communication pipe 103 communicate with the connection port 76b different from the connection port 76a. At the same time, the anti-communicating pipe line 103 side is connected to the connecting port 76b side of the indoor heat exchanger 27 (in other words, the outlet side during heating operation, etc., the same applies hereinafter; see FIG. 10, etc. described later) Is included. As a result, the two-way valve 122 has a function of opening and closing a pipe line between the pipe portion 26a on the side of the anti-expansion valve 112 of the indoor heat exchanger 27 and the compressor 14, and the two-way valve 124. Is provided with a function of opening and closing a pipe line between the piping part 26 a on the side of the anti-expansion valve 112 of the indoor heat exchanger 27 and the expansion valve 113. The communication line 103 has a function of communicating the expansion valve 112 with the expansion valve 112 side of the indoor heat exchanger 27, and the communication line 104 includes the two-way valves 122 and 124 and the The indoor heat exchanger 27 has a function of communicating with the anti-expansion valve 112 side. In other words, the hot water storage unit 100 and the air conditioner unit 200 are connected by the communication conduits 103 and 104 (see also FIG. 1).

  The indoor heat exchanger 27, the indoor fan 77, and the like are included in the casing of the air conditioner unit 200 (see FIG. 1).

  Note that, as described above in the above description, the piping part 18b and the piping part 25a function as a discharge side pipe connected to the discharge side of the compressor 14, and the pipe parts 25b and 25c are the discharge side pipes. Branching from a predetermined branch point D and functioning as a first pipe having the water-refrigerant heat exchanger 15 disposed therein, and pipe portions 25d1, 25d2, 26a, 26b, and 25g are connected to the discharge side. The pipe 25a, 25e1, 18e is connected to the pipe branching from the branch point D and functions as a second pipe provided with the indoor heat exchanger 27. The water refrigerant heat exchanger 15 A third pipe that connects a junction E at which the first pipe on the downstream side and the second pipe on the downstream side of the indoor heat exchanger 27 join to the inlet side of the outdoor heat exchanger 17. And the piping portions 18d and 18c are It serves the outlet side of the external heat exchanger 17 as a suction side pipe line for connecting the suction side of the compressor 14

  In the refrigerant circuit 30, for example, R32 refrigerant is used as a refrigerant to constitute a heat pump cycle. The refrigerant may be an HFC refrigerant, an HFO refrigerant, or a carbon dioxide refrigerant. And in the refrigerant | coolant piping 18 of the said heat-pon circuit part 30A, the discharge temperature sensor 20 which detects the refrigerant | coolant discharge temperature Tout discharged from the compressor 14 is provided in the said piping part 18a, The said piping part 18c has A suction temperature sensor 32 that detects the refrigerant suction temperature Tin of the refrigerant sucked into the compressor 14 is provided. An outdoor air temperature sensor 22 for detecting the outdoor air temperature Tair is provided on the air inlet side of the outdoor heat exchanger 17, and the heat exchanger heat exchange temperature Tex (acts as an evaporator) in the outdoor heat exchanger 17. A heat exchange temperature sensor 35 is provided for detecting the temperature of the evaporative refrigerant during The detection results of these sensors 20, 32, 22, and 35 are input to a heat pump control unit 410 provided in the heat pump unit 300 and further provided in the hot water storage control unit 420 and the air conditioner unit 200 provided in the hot water storage unit 100 as appropriate. It is also input to the air conditioner control unit 430 (which may be received via the heat pump control unit 410 or may be received directly from the sensors 20, 32, 22).

  In addition, in the refrigerant pipe 25 of the hot water storage circuit section 30B, the pipe section 25c is provided with an outflow temperature sensor 21 that detects the refrigerant outflow temperature T2 that flows out from the refrigerant-side flow path 15b and travels toward the expansion valve 111. It has been. The water refrigerant heat exchanger 15 is provided with a condensing temperature sensor 33 that detects a refrigerant condensing temperature when the refrigerant condenses in the flow path 15b on the refrigerant side. The detection results of these sensors 21 and 33 are input to a hot water storage control unit 420 provided in the hot water storage unit 100, and further, the heat pump control unit 410 provided in the heat pump unit 300 and the air conditioner unit 200 as appropriate. It is also input to the air conditioner control unit 430 (may be received via the hot water storage control unit 420 or may be received directly from the sensors 21 and 33).

  Further, with respect to the refrigerant pipe 26 of the air conditioner circuit section 30C, the indoor heat exchanger 27 is provided with an indoor temperature sensor 34 for detecting the indoor temperature Tr of the air-conditioning target space. The detection result of the sensor 34 is input to an air conditioner control unit 430 provided in the air conditioner unit 200, and further, the heat pump control unit 410 provided in the heat pump unit 300 and the hot water storage control unit provided in the hot water storage unit 100 as appropriate. It is also input to 420 (may be received via the air conditioner control unit 430 or directly from the sensor 34).

  The hot water storage control unit 420 of the hot water storage unit 100, the heat pump control unit 410 of the heat pump unit 300, and the air conditioner control unit 430 of the air conditioner unit 200 are connected to be communicable with each other. Based on the detection result, the operation of each device / actuator in the hot water storage unit 100, the heat pump unit 300, and the air conditioner unit 200 is controlled in cooperation with each other. In particular, the hot water in the hot water storage tank 2 is heated by controlling the opening / closing operation and the opening degree of the two-way valves 121, 122, 123, and 124 and the expansion valves 111, 112, and 113 and switching the flow path of the refrigerant. (Supplying heated hot water) and performing boiling operation, cooling operation for cooling the air-conditioned space, heating operation for heating the air-conditioned space, boiling and cooling in parallel The boiling / cooling operation performed in this manner, and the boiling / heating operation performed in parallel with the boiling and heating can be selectively executed.

  At this time, the air conditioner unit 200 can be operated by an appropriate operation unit 60 (hereinafter simply referred to as “remote controller 60”) such as a remote controller. That is, the remote controller 60 is connected to, for example, the air conditioner control unit 430 so as to be able to transmit and receive information, and the user manually operates the remote controller 60 appropriately to thereby perform the above-described boiling operation, cooling operation, and heating. It is possible to instruct which driving operation is performed. Regarding boiling / cooling operation (or boiling / heating operation), when the user gives an instruction for the cooling operation (or heating operation) via the remote controller 60, the state of hot water storage in the hot water storage tank 2 (unheated water) Depending on the amount of the water and the like) and automatically switching to the boiling / cooling operation (or boiling / heating operation) as appropriate. Further, by appropriate operation on the remote controller 60, the boiling mode during the boiling operation (for example, the strong boiling mode, the normal boiling mode, etc.), and the air conditioner operation mode (for example, the powerful mode) during the cooling operation or heating operation. Mode, normal mode, power saving mode, etc.), air conditioner set temperature Tcon, etc. can also be instructed. The contents of instructions from these remote controllers 60 are input to the air conditioner control unit 430 provided in the air conditioner unit 200, and further, the heat pump control unit 410 provided in the heat pump unit 300 and the hot water storage unit 100 as appropriate. It is also input to hot water storage control unit 420 (may be received via air conditioner control unit 430 or may be received directly from remote control 60).

  Next, the heat pump control unit 410 provided in the heat pump unit 300 will be described. Although not shown in detail, the heat-pon control unit 410 includes a storage unit that stores various data and programs, and a control unit that performs calculation / control processing. The functional configuration of the heat-pon control unit 410 will be described with reference to FIG.

  As shown in FIG. 3, the heat pump control unit 410 includes a four-way valve control unit 410A, a compressor control unit 410B, an expansion valve control unit 410C as discharge temperature control means, and an outdoor fan control unit 410D. In preparation.

  The four-way valve control unit 410A is instructed by the remote controller 60 as to which operation to perform (boiling operation, cooling operation, heating operation), and the hot water storage temperature detected by the hot water storage temperature sensor 12. Are entered. The four-way valve control unit 410A actually operates the heat pump water heater 1 in accordance with the operation instruction and the heating state (hot water storage state) of the hot water corresponding to the hot water storage temperature (boiling operation, cooling operation). Operation, boiling / cooling operation, heating operation, boiling / heating operation), and corresponding operation information includes the compressor control unit 410B, the expansion valve control unit 410C, the outdoor fan control unit 410D, And it outputs to the hot water storage control part 420 and the air-conditioner control part 430. The four-way valve control unit 410A outputs an opening / closing signal corresponding to the determined operation mode to the four-way valve 31, and switches the four-way valve 31 (detailed control content will be described later).

  The compressor control unit 410B includes the outside air temperature Tair detected by the outside air temperature sensor 22, the indoor temperature Tr detected by the indoor temperature sensor 34, and the air conditioner set temperature Tcon set by the remote controller 60. And the boiling mode are input (in addition to the case of direct input, the indirect input is also included, and so on). The compressor control unit 410B is input from the four-way valve control unit 410A as described above (any of boiling operation, cooling operation, boiling / cooling operation, heating operation, and boiling / heating operation is performed). The number of rotations of the compressor 14 is controlled based on at least one of the input temperature and setting according to the operation information (detailed control content will be described later). In addition, the rotation speed (target rotation speed as a control value) of the compressor 14 at this time is also output to an expansion valve control unit 420B of a hot water storage control unit 420 (not shown).

  The expansion valve control unit 410C includes the refrigerant discharge temperature Tout detected by the discharge temperature sensor 20, the refrigerant outflow temperature T2 detected by the outflow temperature sensor 21, and the intake temperature sensor 32. The refrigerant suction temperature Tin and the heat-pon heat exchange temperature Tex detected by the heat exchange temperature sensor 35 are input. The expansion valve control unit 410C controls the opening of the expansion valve 113 based on at least one of the input temperatures in accordance with the operation information from the four-way valve control unit 410A (detailed control). The contents will be described later).

  The outdoor fan control unit 410D receives the outside air temperature Tair detected by the outside air temperature sensor 22 and the air conditioner operation mode set by the remote controller 60. The outdoor fan control unit 410D responds to the operation information from the four-way valve control unit 410A, and with respect to the outdoor fan 67 according to the outside air temperature Tair and the operation mode, the target rotation speed N2 (hereinafter, as appropriate, A drive control signal corresponding to “outdoor fan rotation speed N2” (similarly shown in the figure) is output, and thereby the rotation speed of the outdoor fan 67 is variably controlled (detailed control content will be described later).

  The operation mode may be determined by the hot water storage control unit 420 or the air conditioner control unit 430. In this case, the operation information corresponding to the determined operation mode is input to the heat pump control unit 410 from the hot water storage control unit 420 and the air conditioner control unit 430, and the four-way valve control unit 410A according to the input operation information. The compressor control unit 410B, the expansion valve control unit 410C, and the outdoor fan control unit 410D perform various controls.

  Next, the hot water storage control unit 420 provided in the hot water storage unit 100 will be described. The hot water storage control unit 420 includes a storage unit and a control unit, similar to the heat pump control unit 410, and its functional configuration will be described with reference to FIG.

  As shown in FIG. 4, the hot water storage control unit 420 functionally includes a pump control unit 420A, an expansion valve control unit 420B as a diversion control unit, and a two-way valve control unit 420C.

  The operation information from the heat pump control unit 410 and the boiling temperature Tb detected by the boiling temperature sensor 24 are input to the pump control unit 420A. The pump control unit 420A is input from the heat pump control unit 410 as described above (whether boiling operation, cooling operation, boiling / cooling operation, heating operation, or boiling / heating operation is performed). The number of rotations of the boiling pump 19 is controlled based on the inputted boiling temperature Tb in accordance with the operation information (detailed control content will be described later).

  The expansion valve control unit 420B includes the operation information from the heat pump control unit 410, the outside air temperature Tair detected by the outside air temperature sensor 22, the air conditioner operation mode set by the remote controller 60, and the heat pump. The rotation speed of the compressor 14 input from the compressor control section 410B of the control section 410 (the target rotation speed; however, the actual rotation speed of the compressor 14 detected by a known method may be input). The refrigerant outflow temperature T2 detected by the outflow temperature sensor 21, the refrigerant intake temperature Tin detected by the intake temperature sensor 32, and the refrigerant discharge temperature Tout detected by the discharge temperature sensor 20. Entered. The expansion valve control unit 420B is configured to open the openings of the expansion valves 111 and 112 based on at least one of the input temperature, mode setting, and rotation speed in accordance with the operation information from the heat pump control unit 410. (Details of control contents will be described later).

  The operation information from the heat pump control unit 410 is input to the two-way valve control unit 420C. The two-way valve control unit 420C controls the opening / closing operation of the two-way valves 121, 122, 123, and 124 based on the operation information (detailed control content will be described later).

  As described above, the operation mode may be determined in the hot water storage control unit 420 (for example, the two-way valve control unit 420C) or the air conditioner control unit 430. In this case, the pump control unit 420A, the expansion valve control unit 420B, and the two-way valve control unit 420C perform various controls according to the operation information corresponding to the operation mode determined by the two-way valve control unit 420C and the air conditioner control unit 430. I do.

  Next, the air conditioner control unit 430 provided in the air conditioner unit 200 will be described. The air conditioner control unit 430 includes a storage unit and a control unit, similar to the heat pump control unit 410 and the hot water storage control unit 420, and its functional configuration will be described with reference to FIG.

  As shown in FIG. 5, the air conditioner control unit 430 functionally includes an indoor fan control unit 430A.

  The indoor fan control unit 430A receives the operation information from the heat-pump control unit 410, the indoor temperature Tr detected by the indoor temperature sensor 34, and the air conditioner set temperature Tcon set by the remote controller 60. Is done. The indoor fan control unit 430A responds to the operation information from the heat-pump control unit 410, and with respect to the indoor fan 77 according to the indoor temperature Tr and the air conditioner set temperature Tcon (hereinafter, as appropriate) A drive control signal corresponding to “indoor fan rotational speed N1” (similarly shown in the figure) is output, and thereby the rotational speed of the indoor fan 77 is variably controlled (detailed control content will be described later).

  As described above, the operation mode may be determined in the air conditioner control unit 430 or the hot water storage control unit 420. In this case, the indoor fan control unit 430A performs the control according to the operation information corresponding to the operation mode determined by the air conditioner control unit 430 and the hot water storage control unit 420.

  As described above, the heat pump water heater 1 according to the present embodiment can selectively execute five types of operation including boiling operation, cooling operation, heating operation, boiling / cooling operation, and boiling / heating operation. . Hereinafter, details of each operation will be sequentially described.

  First, boiling operation will be described with reference to FIG. In the boiling operation shown in FIG. 6, the four-way valve control unit 410A causes the four-way valve 31 to connect the pipe part 18a to the pipe part 18b and to connect the pipe part 18c to the pipe part 18d. The position is switched to the heating position (the heating side described above). The two-way valve controller 420C switches the two-way valve 121 to the open state, the two-way valve 122 to the closed state, the two-way valve 123 to the open state, and the two-way valve 124 to the closed state. Further, the expansion valve control unit 420B controls the expansion valve 111 to be in a fully open state and the expansion valve 112 to be in a fully closed state, and the expansion valve control unit 410C opens the expansion valve 113 (details will be described later as ΔH Is being controlled).

  As a result, the discharge side piping section 18a → the piping section 18b → the communication pipe 101 → the piping section 25a → the piping section 25b → the refrigerant side flow path 15b of the water refrigerant heat exchanger 15 → the piping section 25c (expansion). Valve 111) → pipe part 25e2 → pipe part 25e1 → communication pipe line 102 → pipe part 18e (expansion valve 113) → outdoor heat exchanger 17 → pipe part 18d → the refrigerant path of the pipe part 18c on the suction side of the compressor 14 It is formed. Thereby, after the refrigerant in the gas state sucked at low temperature and low pressure is compressed by the compressor 14 to become high temperature and high pressure gas, the flow on the refrigerant side of the water refrigerant heat exchanger 15 functioning as a condenser is performed. In the channel 15b, heat exchange is performed with the water flowing through the water-side channel 15a to release heat to the water and change into a high-pressure liquid while heating. The refrigerant thus turned into a liquid is decompressed by the expansion valve 113 through the fully opened expansion valve 111 and becomes a low-temperature / low-pressure liquid and easily evaporates. In the outdoor heat exchanger 17 functioning as an evaporator, The heat is exchanged with the outside air to evaporate and change into gas, thereby absorbing heat and returning to the compressor 14 again as a low temperature / low pressure gas. At this time, the low-temperature water (unheated water) taken out from the heating forward pipe 5 connected to the lower part of the hot water storage tank 2 receives heat from the condensing refrigerant in the water-side flow path 15a of the water-refrigerant heat exchanger 15. Then, after being heated to a high temperature, the hot water is returned to the hot water storage tank 2 from the heating return pipe 6 connected to the upper part of the hot water storage tank 2 so that the hot water (heated water) is sequentially stored in the hot water storage tank 2 in a laminated form. The

  In the above operation, the target rotational speed of the compressor 14 (hereinafter, appropriately referred to as “target rotational speed Nb” during the boiling operation) is based on the outside air temperature Tair under the control of the compressor control unit 410B. It is determined. That is, for example, as shown by the downward-sloping characteristic line in FIG. 7A, when the outside air temperature Tair is low, the target rotational speed Nb is controlled to be large, and when the outside air temperature Tair is high, the target rotational speed Nb is small. It is controlled to become. The outdoor fan rotation speed N2 of the outdoor fan 67 is determined based on the outdoor air temperature Tair under the control of the outdoor fan control unit 410D. That is, when the outside air temperature Tair is low, the fan rotation speed is controlled to be large, and when the outside air temperature Tair is high, the fan rotation speed is controlled to be small.

  Returning to FIG. 6, the rotation speed of the boiling pump 19 is feedback-controlled by the control of the pump control unit 420 </ b> A so that the boiling temperature Tb becomes a predetermined target temperature. That is, when the boiling temperature Tb is lower than the target temperature, control is performed such that the pump rotational speed is decreased (the flow rate is decreased), and when the boiling temperature Tb is higher than the target temperature, the pump rotational speed is increased (the flow rate is decreased). To be increased). The indoor fan 77 is stopped from rotating under the control of the indoor fan control unit 430A.

  The opening degree of the expansion valve 113 is variably controlled by the expansion valve control unit 410C according to the operating state of the boiling operation. Specifically, the opening of the expansion valve 113 is set at a predetermined cycle so that the temperature difference ΔH = Tout−T2 between the refrigerant discharge temperature Tout and the refrigerant outflow temperature T2 becomes a predetermined target temperature difference ΔHm. Perform feedback control (ΔH control). That is, the expansion valve control unit 410C controls the opening degree of the expansion valve 113 to close when ΔH <ΔHm, and opens the opening degree of the expansion valve 113 when ΔH> ΔHm. If ΔH = ΔHm, the opening degree of the expansion valve 113 is maintained as it is. Alternatively, instead of the ΔH control, the opening degree of the expansion valve 113 may be feedback controlled so that the refrigerant discharge temperature Tout becomes a predetermined constant value (discharge control). In this case, the expansion valve control unit 410C controls the opening degree of the expansion valve 113 to close when the refrigerant discharge temperature Tout is too low, and opens the opening degree of the expansion valve 113 when the refrigerant discharge temperature Tout is too high. Control in the direction.

  Next, the cooling operation will be described with reference to FIG. In the cooling operation shown in FIG. 8, the four-way valve control unit 410A causes the four-way valve 31 to connect the pipe part 18a to the pipe part 18d and to connect the pipe part 18c to the pipe part 18b. It is switched to a position (cooling side different from the heating side). The two-way valve controller 420C switches the two-way valve 121 to the closed state, the two-way valve 122 to the open state, the two-way valve 123 to the open state, and the two-way valve 124 to the closed state. Further, the expansion valve control unit 420B controls the expansion valve 111 to be in a fully closed state and the expansion valve 112 to be in an open state (specifically, feedforward control described below is performed), and the expansion valve control The expansion valve 113 is controlled to be fully opened by the portion 410C.

  As a result, the discharge side piping portion 18a → the piping portion 18d → the outdoor heat exchanger 17 → the piping portion 18e (expansion valve 113) → the communication conduit 102 → the piping portion 25e1 → the piping portion 25e2 → the piping portion 25g ( Expansion valve 112) → Communication conduit 103 → Pipe portion 26b → Indoor heat exchanger 27 → Pipe portion 26a → Communication conduit 104 → Pipe portion 25d2 → Pipe portion 25d1 → Pipe portion 25a → Communication conduit 101 → Pipe portion 18b → A refrigerant path of the piping portion 18c on the suction side of the compressor 14 is formed. Thereby, after the refrigerant in the gas state sucked at low temperature and low pressure is compressed by the compressor 14 to become high temperature and high pressure gas, the outdoor heat exchanger functioning as a condenser with the rotational driving of the outdoor fan 67. In 17, heat is exchanged with the outside air to release heat and change to a high-pressure liquid. The refrigerant that has become liquid in this manner is decompressed by the expansion valve 112 through the fully opened expansion valve 113 and becomes a low-temperature / low-pressure liquid that easily evaporates, and functions as an evaporator when the indoor fan 77 is driven to rotate. The indoor heat exchanger 27 absorbs heat from the indoor air, evaporates and changes to gas, thereby cooling the air-conditioning target space and returns to the compressor 14 again as low-temperature and low-pressure gas.

  In the above operation, the rotation speed of the compressor 14 is determined based on the difference between the room temperature Tr and the air conditioner set temperature Tcon under the control of the compressor control unit 410B. That is, when the value of Tcon-Tr is large, the compressor rotational speed is controlled to be large, and when the value of Tcon-Tr is small, the compressor rotational speed is controlled to be small. The outdoor fan rotation speed N2 of the outdoor fan 67 is controlled by the outdoor fan control unit 410D so that the fan rotation speed is increased when the air conditioner operation mode is, for example, the high power mode. In this case, the fan speed is controlled to be small. Further, in each air-conditioner operation mode, control is performed so that the fan speed decreases when the outside air temperature Tair is low, and the fan speed increases when the outside air temperature Tair is high. The indoor fan rotation speed N1 of the indoor fan 77 is controlled by the indoor fan control unit 430A so that the value of the Tcon-Tr increases so that the fan rotation speed increases when the Tcon-Tr value is large. When it is small, the fan speed is controlled to be small. The boiling pump 19 is stopped from rotating under the control of the pump control unit 420A.

  The opening degree of the expansion valve 112 is variably controlled by the expansion valve control unit 420B according to the operating state of the cooling operation. That is, it is determined based on the outside air temperature Tair, the air conditioner operation mode, and the rotational speed of the compressor 14. That is, the expansion valve control unit 420B determines whether the outside air temperature Tair is high or low and the compressor from the compressor control unit 410B in each of the plurality of air conditioner operation modes (for example, the strong mode, the normal mode, and the power saving mode). The opening degree of the expansion valve 112 is feedforward controlled in consideration of the rotational speed (details are omitted).

  Next, boiling and cooling operation will be described with reference to FIG. In the boiling / cooling operation shown in FIG. 9, the four-way valve control unit 410A switches the four-way valve 31 to the heating side (not the cooling side). Further, the two-way valve controller 420C switches the two-way valve 121 to the open state, the two-way valve 122 to the closed state, the two-way valve 123 to the closed state, and the two-way valve 124 to the open state. Further, the expansion valve control unit 420B controls the expansion valve 111 to be in a fully open state and the expansion valve 112 to be in an open state (detailed below, ΔH control is performed). The expansion valve 113 is controlled to be fully opened by the portion 410C.

  As a result, the refrigerant path is the piping side 18a on the discharge side of the compressor 14 → the piping part 18b → the communication pipe 101 → the piping part 25a → the piping part 25b → the flow path 15b on the refrigerant side of the water refrigerant heat exchanger 15 → the piping. Part 25c (expansion valve 111) → piping part 25g (expansion valve 112) → communication pipe line 103 → piping part 26b → indoor heat exchanger 27 → piping part 26a → communicating pipe line 104 → piping part 25d2 → piping part 25f → piping Portion 25e1 → Communication pipeline 102 → Pipe portion 18e (expansion valve 113) → Outdoor heat exchanger 17 → Pipe portion 18d → Pipe portion 18c on the suction side of the compressor 14

  Thus, after the refrigerant in the gas state sucked at low temperature and low pressure is compressed by the compressor 14 to become high temperature and high pressure gas, first, the water refrigerant heat exchanger 15 (functioning as a condenser) is used in the same manner as described above. The high-temperature water (heated water) is sequentially supplied into the hot water storage tank 2 by heating the water flowing through the water-side flow path 15a and the liquid refrigerant passes through the expansion valve 111 in a fully opened state. The expansion valve 112 is depressurized to become a low-temperature / low-pressure liquid and easily evaporates. When the indoor fan 77 is driven to rotate, the indoor heat exchanger 27 functioning as an evaporator absorbs heat from the indoor air and evaporates. The air-conditioning target space is cooled by changing to the above, and further, through the expansion valve 113, the outdoor fan 67 rotates and exchanges heat with the outside air in the outdoor heat exchanger 17 that functions as an evaporator. Evaporated to me it absorbs heat by varying the gas returns to the compressor 14 as a low-temperature low-pressure gas.

  In the above operation, the rotation speed of the compressor 14 is determined based on the difference between the room temperature Tr and the air conditioner set temperature Tcon, similar to that during the cooling operation, under the control of the compressor control unit 410B. Further, the rotation speed of the outdoor fan 67 is controlled by the outdoor fan control unit 410D, as in the cooling operation, so that the fan rotation speed increases when the outdoor air temperature Tair is low in each air conditioner operation mode. When the Tair is high, the fan rotation speed is controlled to be small, but the rotation speed is controlled to be lower than that during the cooling operation by an appropriate method.

  The number of revolutions of the boiling pump 19 is controlled by the pump control unit 420A, as in the above-described boiling operation, when the boiling temperature Tb is lower than the target temperature, the number of revolutions of the pump becomes small, and the boiling temperature Tb is When the temperature is higher than the target temperature, the pump speed is controlled to be large. The indoor fan rotation speed N1 of the indoor fan 77 is controlled by the indoor fan control unit 430A based on the difference between the indoor temperature Tr and the air conditioner set temperature Tcon, as in the heating operation or the like. When the value of is large, the fan rotational speed is increased, and when the value of Tcon-Tr is small, the fan rotational speed is decreased.

  The opening degree of the expansion valve 112 is variably controlled by the expansion valve control unit 420B in accordance with the operating state of the boiling / cooling operation. Specifically, similar to the control to the expansion valve 113 by the expansion valve control unit 410C during the boiling operation, the temperature difference ΔH = Tout−T2 between the refrigerant discharge temperature Tout and the refrigerant outflow temperature T2 is a predetermined value. The opening degree of the expansion valve 112 is feedback-controlled at a predetermined cycle so that the target temperature difference ΔHm is obtained (ΔH control). That is, the expansion valve control unit 420B controls the opening degree of the expansion valve 112 to close when ΔH <ΔHm, and opens the opening degree of the expansion valve 112 when ΔH> ΔHm. If ΔH = ΔHm, the opening degree of the expansion valve 112 is maintained as it is. Alternatively, instead of this ΔH control, the opening degree of the expansion valve 112 may be feedback controlled so that the refrigerant discharge temperature Tout becomes a predetermined constant value (discharge control). In this case, the expansion valve control unit 420B controls the opening degree of the expansion valve 112 to close when the refrigerant discharge temperature Tout is too low, and opens the opening degree of the expansion valve 112 when the refrigerant discharge temperature Tout is too high. Control in the direction.

  Next, the heating operation will be described with reference to FIG. In the heating operation shown in FIG. 10, the four-way valve 31 is switched to the heating side by the four-way valve control unit 410A as in the boiling operation. Further, the two-way valve control unit 420C switches the two-way valve 121 to the closed state, the two-way valve 122 to the opened state, the two-way valve 123 to the opened state, and the two-way valve 124 to the closed state, as in the cooling operation. It is done. Further, the expansion valve control unit 420B controls the expansion valve 111 to be fully closed and the expansion valve 112 to be fully open, and the expansion valve control unit 410C opens the expansion valve 113 (detailed below is SH control). Is controlled).

  As a result, the discharge-side piping section 18a → the piping section 18b → the communication pipe 101 → the piping section 25a → the piping section 25d1 → the piping section 25d2 → the communication pipe 104 → the piping section 26a → the indoor heat exchanger 27 → Piping part 26b → Communication pipe line 103 → Piping part 25g (expansion valve 112) → Piping part 25e2 → Piping part 25e1 → Communication pipe line 102 → Pipe part 18e (expansion valve 113) → Outdoor heat exchanger 17 → Pipe part 18d → A refrigerant path of the piping portion 18c on the suction side of the compressor 14 is formed. As a result, after the refrigerant in the gas state sucked at low temperature and low pressure is compressed by the compressor 14 to become high temperature and high pressure gas, the indoor heat exchanger 27 functioning as a condenser exchanges heat with the indoor air. The heat is released to change into a high-pressure liquid while heating the air-conditioning target space. The refrigerant thus turned into a liquid is decompressed in the expansion valve 113 through the fully opened expansion valve 112 and becomes a low-temperature / low-pressure liquid and easily evaporates. In the outdoor heat exchanger 17 functioning as an evaporator, The heat is exchanged with the outside air to evaporate and change into gas, thereby absorbing heat and returning to the compressor 14 again as a low temperature / low pressure gas.

  In the above operation, the target rotational speed of the compressor 14 (hereinafter referred to as “target rotational speed Nh” as appropriate during heating operation) is controlled by the compressor control unit 410B. The value of the temperature difference ΔT (= Tr−Tcon) so that the target rotational speed is increased when the value of the set temperature Tcon (= temperature difference ΔT; hereinafter simply referred to as “temperature difference ΔT”) is large. When is small, the target rotational speed is controlled to be small. Specifically, in this example, as shown in FIG. 7B, the range of the temperature difference ΔT is set to ΔT ≦ 2 [° C.], 2 <ΔT ≦ 5 [° C.], 5 <ΔT. ≦ 10 [° C.], 10 <T [° C.].

  When the temperature difference ΔT is the smallest ΔT ≦ 2 [° C.] of the four sections, the compressor control unit 410B sets the target rotational speed Nh of the compressor 14 to 20 [rpm. ] Is controlled. In addition, when the temperature difference ΔT is in the range of 2 <ΔT ≦ 5 [° C.], which is the second smallest among the four sections, the compressor control unit 410B causes the target rotational speed Nh of the compressor 14 to be Is controlled to 30 [rpm]. Further, when the temperature difference ΔT is in the range of 5 <ΔT ≦ 10 [° C.], which is the second largest among the four sections, the compressor control unit 410B causes the target rotational speed Nh of the compressor 14 to be increased. Is controlled to 40 [rpm]. When the temperature difference ΔT is in the range of 10 <ΔT [° C.] which is the largest among the four sections, the compressor control unit 410B sets the target rotational speed Nh of the compressor 14 to 50 [rpm. ] Is controlled.

  Returning to FIG. 10, the outdoor fan rotation speed N2 of the outdoor fan 67 is determined based on the outdoor air temperature Tair and the air conditioner operation mode under the control of the outdoor fan control unit 410D. That is, in each of a plurality of prepared air conditioner operation modes (for example, the high power mode, the normal mode, the power saving mode, etc.), when the outside air temperature Tair is low, the fan speed is controlled to increase, and when the outside air temperature Tair is high. The fan speed is controlled to be small.

  The indoor fan rotation speed N1 in the indoor fan 77 is determined based on the temperature difference ΔT, that is, the difference between the indoor temperature Tr and the air conditioner set temperature Tcon, under the control of the indoor fan control unit 430A. That is, when the value of Tcon-Tr is large, control is performed so that the fan rotational speed is increased, and when the value of Tcon-Tr is small, control is performed so that the fan rotational speed is decreased. The boiling pump 19 is stopped from rotating under the control of the pump control unit 420A.

  The opening degree of the expansion valve 113 is variably controlled by the expansion valve control unit 410C according to the operating state of the heating operation. Specifically, the opening degree of the expansion valve 113 is feedback-controlled so that the temperature difference Tin-Tex between the refrigerant suction temperature Tin and the heat-pump heat exchange temperature Tex becomes a predetermined constant value (SH control). That is, the expansion valve control unit 410C controls the opening of the expansion valve 113 to close when Tin-Tex is too small, and controls the opening of the expansion valve 113 to open when Tin-Tex is too large. To do.

  Next, boiling and heating operation will be described with reference to FIG. Also in the boiling / heating operation shown in FIG. 11, the four-way valve control unit 410A switches the four-way valve 31 to the heating side. The two-way valve controller 420C switches the two-way valve 121 to the open state, the two-way valve 122 to the open state, the two-way valve 123 to the open state, and the two-way valve 124 to the closed state. Further, the expansion valve control unit 420B controls the expansion valve 113 to be in an open state (specifically, discharge control described later is performed), and the expansion valve 111 and the expansion valve 112 are connected to the expansion valve control unit 410C. Thus, the opening degree is variably controlled by diversion control (details will be described later) for distributing and supplying the refrigerant to the water-refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side at a desired ratio (diversion ratio).

  As a result, the refrigerant path is divided into two at the branch point D via the piping part 18a on the discharge side of the compressor 14 → the piping part 18b → the communication pipe 101 → the piping part 25a. Part 25b → flow path 15b on the refrigerant side of the water-refrigerant heat exchanger 15 → pipe part 25c (expansion valve 111) to reach the junction point E, and the other is a branch point D → pipe part 25d1 → pipe part 25d2 → communication. The pipe 104 → the piping section 26a → the indoor heat exchanger 27 → the piping section 26b → the communication pipe 103 → the piping section 25g (expansion valve 112) to the junction point E, and at the junction point E, the water-refrigerant heat exchanger Join the route from 15. The subsequent path is: junction E → pipe part 25e2 → pipe part 25e1 → communication pipe line 102 → pipe part 18e (expansion valve 113) → outdoor heat exchanger 17 → pipe part 18d → pipe part on the suction side of the compressor 14 18c.

  As a result, the refrigerant in the gas state sucked at a low temperature and a low pressure is compressed by the compressor 14 to become a high temperature and a high pressure gas, and then divided as described above, and the one flow is the water refrigerant heat exchanger. 15 (functions as a condenser) is condensed in the same manner as described above to heat the water flowing through the water-side flow path 15a, thereby supplying hot water (heated water) sequentially into the hot water storage tank 2, and the other flow is In the indoor heat exchanger 27 (functioning as a condenser), the air-conditioning target space is heated by condensing in the same manner as described above and releasing heat to the indoor air. The refrigerant that has changed into a high-pressure liquid by condensation in the heat exchangers 15 and 27 is decompressed by the expansion valve 113 to become a low-temperature / low-pressure liquid, and then in the outdoor heat exchanger 17 (functions as an evaporator). It evaporates and absorbs heat from the outside air, and returns to the compressor 14 again as a low temperature / low pressure gas.

  In the above operation, the rotational speed of the compressor 14 is determined based on the outside air temperature Tair under the control of the compressor control unit 410B. The target rotational speed Nb during the boiling operation (see FIG. 7A). ) And the target rotational speed Nh (see FIG. 7B) determined during the heating operation determined based on the temperature difference ΔT (= air conditioner set temperature Tcon−room temperature Tr). Control is performed so that the target rotational speed is Nbh (= Nb + Nh). That is, as shown in FIG. 7C, in this example, in the four characteristic lines (broken line, one-dot chain line, dotted line, two-dot chain line in order from the bottom) as shown in the figure, the temperature difference ΔT As the value becomes larger, the characteristic line to be used is switched in stages so that the characteristic line on the higher rotation speed side is obtained.

  Specifically, as shown in FIG. 7C, when the temperature difference ΔT is in the range of ΔT ≦ 2 [° C.], the compressor control unit 410B sets the target rotational speed Nbh. FIG. 7 (a) is obtained by adding 20 [rpm] shown in FIG. 7 (b) to the target rotation speed Nb during the boiling operation shown by a solid line (same as the solid line in FIG. 7 (a)) as a control reference. c) Control is performed so that the characteristic indicated by the broken line in FIG. 5 is obtained (that is, Nbh = Nb + 20). When the temperature difference ΔT is in the range of 2 <ΔT ≦ 5 [° C.], the compressor control unit 410B sets the target rotational speed Nbh as the target during the boiling operation indicated by a solid line. Control is performed so that the rotation speed Nb has the characteristics indicated by the alternate long and short dash line in FIG. 7C obtained by adding 30 [rpm] shown in FIG. 7B (that is, Nbh = Nb + 30). Furthermore, when the temperature difference ΔT is in the range of 5 <ΔT ≦ 10 [° C.], the compressor control unit 410B sets the target rotational speed Nbh to the target during the boiling operation indicated by a solid line. Control is performed so that the characteristic indicated by the dotted line in FIG. 7C is obtained by adding 40 [rpm] shown in FIG. 7B to the rotational speed Nb (that is, Nbh = Nb + 40). Further, when the temperature difference ΔT is in the range of 10 <ΔT [° C.], the compressor control unit 410B sets the target rotational speed Nbh to the target rotational speed during the boiling operation indicated by a solid line. Control is performed so that Nb has a characteristic indicated by a two-dot chain line in FIG. 7C obtained by adding 50 [rpm] shown in FIG. 7B (that is, Nbh = Nb + 50).

  Returning to FIG. 11, the outdoor fan speed N2 is controlled by the outdoor fan control unit 410D based on the outside air temperature Tair and the air conditioner operation mode, as in the heating operation. When the air temperature is low, the fan rotational speed is increased, and when the outside air temperature Tair is high, the fan rotational speed is decreased.

  The number of revolutions of the boiling pump 19 is controlled by the pump control unit 420A, as in the above-described boiling operation, when the boiling temperature Tb is lower than the target temperature, the number of revolutions of the pump becomes small, and the boiling temperature Tb is When the temperature is higher than the target temperature, the pump speed is controlled to be large. The indoor fan rotation speed N1 is controlled by the indoor fan control unit 430A, based on the temperature difference ΔT (= Tr−Tcon), as in the heating operation, and when the value of Tcon−Tr is large, When the value of Tcon-Tr is small, the fan rotational speed is controlled to be small so that the rotational speed is large.

  The opening degree of the expansion valves 111 and 112 is variably controlled by the diversion control by the expansion valve control unit 410C as described above. The details of the control contents of the diversion control will be described with reference to FIGS. 12 (a) and 12 (b).

  FIG. 12A shows an example of a control map for controlling the opening degree of the expansion valve 111, which is executed by the expansion valve control unit 410C. In the maps shown in FIGS. 12A and 12B, the vertical boiling required capacity as the first required heat exchange capacity (in this example, the target rotational speed Nb at the time of boiling as a corresponding index is plotted on the vertical axis. ) In the downward increasing direction, and the horizontal axis indicates the heating required capacity as the second required heat exchange capacity (in this example, the target rotational speed Nh during heating as the corresponding index) in the downward increasing direction, The valve opening value in each state (for example, a relative value in which the fully closed state is “0” and the fully open state is “500”) is shown.

  As shown in FIG. 12 (a), for example, when the required heating capacity is at the minimum level and the required boiling capacity is at the minimum level at the time of boiling / heating operation, the expansion valve 111 has an opening "250". (For example, the opening degree is exactly halfway between fully open and fully closed). When the required heating capacity remains at the minimum level and the required boiling capacity increases by one rank, the opening degree of the expansion valve 111 is controlled to be a slightly larger opening "300", and the required boiling capacity increases by one rank. When it is higher, the opening of the expansion valve 111 is controlled to be a slightly larger opening “350”, and when the boiling-up required capacity is further increased by one rank, the opening of the expansion valve 111 is a slightly larger opening “400”. When the boiling requirement is further increased by one rank, the opening of the expansion valve 111 is controlled to be a slightly larger opening “450” (a state close to a fully opened state). Thus, by gradually increasing the opening degree of the expansion valve 111, the diversion ratio to the water refrigerant heat exchanger 15 side in the diversion to the water refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side increases. To be controlled.

  Similarly, when the required heating capacity is one level higher than the minimum level and the required boiling capacity is the minimum level, the expansion valve 111 has an opening “200” smaller than the opening “250”. To be controlled. Thereby, the diversion ratio to the indoor heat exchanger 27 side in the diversion is slightly increased (compared to the case of the opening degree “250”). In this state, when the required boiling capacity increases by one rank, the opening degree of the expansion valve 111 is controlled to be a slightly larger opening "250", and thereafter, the required boiling capacity increases by one rank. Accordingly, the opening degree of the expansion valve 111 is controlled to gradually increase to “300”, “350”, and “400”, and the diversion ratio toward the water / refrigerant heat exchanger 15 is increased.

  Further, similarly to the above, when the heating required capacity is two ranks higher than the minimum level and the boiling required capacity is the minimum level, the expansion valve 111 has an opening “150” smaller than the opening “200”. It is controlled to become. Thereby, the diversion ratio to the indoor heat exchanger 27 side further increases (compared to the opening degree “200”). In this state, the opening degree of the expansion valve 111 is controlled to gradually increase to “200”, “250”, “300”, and “350” as the required boiling capacity increases by one rank. The diversion ratio to the refrigerant heat exchanger 15 side increases.

  Further, similarly to the above, when the heating required capacity is three ranks higher than the minimum level and the boiling required capacity is at the minimum level, the expansion valve 111 has an opening “100” smaller than the opening “150”. It is controlled to become. Thereby, the diversion ratio to the indoor heat exchanger 27 side further increases (compared to the case of the opening degree “150”). In this state, as the boiling-up required capacity increases by one rank, the opening degree of the expansion valve 111 is controlled to gradually increase to “150”, “200”, “250”, and “300”. The diversion ratio to the refrigerant heat exchanger 15 side increases.

  Further, similarly to the above, when the required heating capacity is the maximum level and the required boiling capacity is the minimum level, the expansion valve 111 has an opening “50” that is smaller than the opening “100”. Be controlled. Thereby, the diversion ratio to the indoor heat exchanger 27 side further increases (compared to the case of the opening degree “100”). In this state, the opening degree of the expansion valve 111 is controlled to gradually increase to “100”, “150”, “200”, and “250” as the boiling-up required capacity increases by one rank. The diversion ratio to the heat exchanger 15 side increases.

  FIG. 12B shows an example of a control map for opening degree control of the expansion valve 112 executed by the expansion valve control unit 410C. In the map shown in FIG. 12B, as described above, the boiling required capacity (target rotational speed Nb during boiling) is increased on the vertical axis, and the heating required capacity (target rotational speed Nh during heating) is increased downward on the horizontal axis. It represents for the direction.

  As shown in FIG. 12 (b), for example, when the required heating capacity at the boiling / heating operation is at the minimum level and the required boiling capacity is also at the minimum level, the expansion valve 112 has the opening degree "250". It is controlled to become. When the required heating capacity remains at the minimum level and the required boiling capacity increases by one rank, the opening degree of the expansion valve 112 is controlled to be a slightly smaller opening "200", and the required boiling capacity increases by one rank. When it is higher, the opening degree of the expansion valve 112 is controlled to be a slightly smaller opening degree “150”, and when the boiling-up required capacity is further increased by one rank, the opening degree of the expansion valve 112 is a little smaller opening degree “100”. When the boiling requirement is further increased by one rank, the opening degree of the expansion valve 112 is controlled to be a slightly larger opening degree “50”. Thus, by gradually decreasing the opening degree of the expansion valve 112, the diversion ratio to the water refrigerant heat exchanger 15 side in the diversion to the water refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side increases. To be controlled.

  Similarly, when the required heating capacity is one level higher than the minimum level and the required boiling capacity is the minimum level, the expansion valve 112 has an opening “300” that is larger than the opening “250”. To be controlled. Thereby, the diversion ratio to the indoor heat exchanger 27 side in the diversion is slightly increased (compared to the case of the opening degree “250”). In this state, when the required boiling capacity increases by one rank, the opening degree of the expansion valve 112 is controlled to be slightly smaller, “250”, and thereafter, the required boiling capacity increases by one rank. Accordingly, the opening degree of the expansion valve 112 is controlled to be gradually reduced to “200”, “150”, and “100”, and the diversion ratio to the water refrigerant heat exchanger 15 side increases.

  Further, similarly to the above, when the heating required capacity is two ranks higher than the minimum level and the boiling required capacity is the minimum level, the expansion valve 112 has an opening “350” larger than the opening “300”. It is controlled to become. Thereby, the diversion ratio to the indoor heat exchanger 27 side is further increased (compared to the case of the opening degree “300”). In this state, as the boiling required capacity increases by one rank, the opening degree of the expansion valve 112 is controlled to gradually decrease to “300” “250” “200” “150” The diversion ratio to the refrigerant heat exchanger 15 side increases.

  Further, similarly to the above, when the required heating capacity is three ranks higher than the minimum level and the required boiling capacity is the minimum level, the expansion valve 112 has an opening “400” that is larger than the opening “350”. It is controlled to become. Thereby, the diversion ratio to the indoor heat exchanger 27 side further increases (compared to the case of the opening degree “350”). In this state, as the boiling-up required capacity increases by one rank, the opening degree of the expansion valve 112 is controlled to gradually decrease to “350”, “300”, “250”, and “200”. The diversion ratio to the refrigerant heat exchanger 15 side increases.

  Further, in the same manner as described above, when the required heating capacity is at the maximum level and the required boiling capacity is at the minimum level, the expansion valve 112 has an opening “450” (a fully open state) larger than the opening “400”. (Close state). Thereby, the diversion ratio to the indoor heat exchanger 27 side is further increased (compared to the opening degree “400”). In this state, the opening degree of the expansion valve 112 is controlled to be gradually reduced to “400”, “350”, “300”, and “250” as the boiling-up required capacity increases by one rank. The diversion ratio to the heat exchanger 15 side increases.

  By the way, in the above boiling / heating operation, according to the study by the inventors of the present application, the expansion valve 111 provided on the water refrigerant heat exchanger 15 side and the indoor heat exchange as described above with reference to FIG. In the diversion balance control only by varying the opening degree of the expansion valve 112 provided on the compressor 27 side, the refrigerant path refrigeration cycle varies greatly as described above, and the refrigerant discharge temperature Tout of the refrigerant discharged from the compressor 14 is stable. It was found not to. That is, as shown in FIG. 13A as a comparative example, in this case, for example, when the operator operates the remote controller 60 to change the air conditioner set temperature Tcon, the heating capacity of the indoor heat exchanger 27 is changed from time t1 to time t1. When switching from WA to WB at t2, the refrigerant discharge temperature Tout rises greatly from the time t1, reaches a peak at Tout = TA at the time t2, and further changes to Tout = tout at a subsequent time t3. After falling sharply to TB, it rises again and finally settles down at time t4, which results in a rather unstable behavior. As a result, the fluctuation range TA-TB of the refrigerant discharge temperature Tout at this time also becomes a relatively large value ΔTAB. As a result, when the refrigerant discharge temperature Tout is too low (for example, Tout = TB at time t3), the heat exchange amount in the water refrigerant heat exchanger 15 is decreased, and the boiling temperature Tb in the heating return pipe 6 is reduced. There is a risk that so-called hot water shortage may occur in the hot water storage tank 2. Further, when the refrigerant discharge temperature Tout is too high (for example, Tout = TA at time t2), the operation may be stopped by a known circuit protection function.

  Accordingly, in this embodiment, in correspondence with this, the expansion provided on the downstream side of the junction E where the refrigerant on the water refrigerant heat exchanger 15 side and the refrigerant on the indoor heat exchanger 27 side merge. In the valve 113, the above discharge control is performed. That is, the opening degree of the expansion valve 113 is feedback-controlled by the expansion valve control unit 410C so that the refrigerant discharge temperature Tout becomes a predetermined constant value. That is, when the refrigerant discharge temperature Tout is too low, the expansion valve control unit 410C controls the opening degree of the expansion valve 113 to close, and when the refrigerant discharge temperature Tout is too high, the opening degree of the expansion valve 113 opens. To be controlled.

  According to this embodiment, by performing such control, as shown in FIG. 13B, the air conditioner set temperature Tcon is changed as described above, and the heating capacity of the indoor heat exchanger 27 is changed over time. Even when switching from Wa to Wb from t1 to t2, the refrigerant discharge temperature Tout rises slightly from the time t1, reaches a peak at Tout = Ta at the time t2, and then falls slightly to a time t5 immediately after Then, after Tout = Tb, it converges stably at time t6 thereafter. As described above, as a result of a stable behavior with less fluctuation compared to the comparative example of FIG. 13A, the fluctuation width Ta-Tb of the refrigerant discharge temperature Tout at this time is also considerably smaller than the ΔTAB. [Delta] stays at Tab. Therefore, unlike the comparative example, while maintaining the high boiling temperature Tb, the diversion balance between the water-refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side is optimally controlled to operate stably. Can continue.

  Further, in the present embodiment, in particular, the boiling requirement capacity on the water refrigerant heat exchanger 15 side (the target rotation speed Nb in the above example) and the heating requirement capacity on the indoor heat exchanger 27 side (the above example). Then, the diversion ratio is controlled by variably controlling the valve openings of the expansion valves 111 and 112 according to the heating target rotation speed Nh). Thereby, a diversion ratio can be changed with high accuracy.

  In the present embodiment, in particular, a two-way valve 121 is provided in addition to the expansion valve 111 in the piping portion 25b, and a two-way valve 122 is provided in addition to the expansion valve 112 in the piping portion 25d1. Thereby, in each of the pipes (pipe parts 25b, 25c, etc.) on the side of the water refrigerant heat exchanger 15 and the pipes (pipe parts 25d1, 25d2, 26a, 26b, 25g) on the indoor heat exchanger 27 side, reliable diversion is performed. Balance control can be performed.

  In addition, this invention is not limited to the said embodiment, A various change is possible in the range which does not change the summary of invention.

  For example, in the above embodiment, the boiling requirement capacity on the water refrigerant heat exchanger 15 side (in the above example, the target rotation speed Nb during boiling) and the heating requirement capacity on the indoor heat exchanger 27 side (in the above example) The valve openings of the expansion valves 111 and 112 were variably controlled according to the heating target rotational speed Nh). Instead of this, only one of the remaining expansion valves may be variably controlled while the valve opening of any one of the expansion valves is fixed.

  As such a modification, control maps by the expansion valve control unit 420B in the case where only the opening degree of the expansion valve 112 is variably controlled while the opening degree of the expansion valve 111 is fixed are shown in FIGS. Shown in b).

  In the maps shown in FIGS. 14 (a) and 14 (b), as in FIG. 12, the vertical axis indicates the required boiling capacity (the target rotational speed Nb during boiling) in the downward increasing direction, and the horizontal axis indicates heating. Value of valve opening in each state when the required capacity (target rotation speed Nh during heating) is increased downward (relative value where the fully closed state is “0” and the fully opened state is “500”) Represents.

  And as shown to Fig.14 (a), in this modification, the expansion valve 111 is the said whether the said heating request capability and the said boiling request capability at the time of boiling-up and heating operation are what level. The opening degree of the expansion valve 111 is fixed to an opening degree “250” (for example, an opening degree that is exactly halfway between full opening and full closing).

  The opening degree of the expansion valve 112 is exactly the same as the control map shown in FIG. 12 (b), as shown in FIG. 14 (b).

  In this modified example, in addition to the effects similar to those of the above-described embodiment, the valve opening degree of the expansion valve 112 on the indoor heat exchanger 27 side is fixed while the valve opening degree of the expansion valve 111 on the water refrigerant heat exchanger 15 side is fixed. By controlling the diversion ratio with variable, there is also an effect that the diversion ratio can be quickly changed with a simple control mode.

  Further, for example, in the above embodiment, as shown in FIG. 11, the two-way valve 121 is arranged on the upstream side of the water / refrigerant heat exchanger 15 at the time of the boiling / heating operation in the piping parts 25 b and 25 c, The two-way valve 122 is arranged on the upstream side of the indoor heat exchanger 27 during the heating and heating operation in the piping portions 25d1, 25d2, 26a, 26b, and 25g. The expansion valve 112 was disposed (see FIG. 11).

  For example, as shown in FIG. 15, the two-way valve 121 is replaced with an expansion valve 121a having a fully-closed function in the piping portions 25b and 25c, and the expansion valve 121a is used as described above. In the piping portions 25d1 and 25g, the two-way valve 122 is replaced with an expansion valve 122a having a fully-closed function, and the diversion ratio is controlled by the expansion valve 122a as described above. Also good. Alternatively, only one of the two exchanges may be performed.

  Furthermore, the present invention is not limited to the above embodiment, and for example, at least one of the two-way valves 121 to 124 may be replaced with an expansion valve with a closing function. Further, instead of the expansion valves 111 to 113, an ejector may be used as a decompressor.

1 Heat pump water heater 2 Hot water storage tank 4 Heating circulation circuit (hot water circulation circuit)
5 Heating pipe (hot water pipe)
6 Heating return pipe (hot water pipe)
DESCRIPTION OF SYMBOLS 14 Compressor 15 Water refrigerant heat exchanger 15a Refrigerant side flow path 15b Water side flow path 17 Outdoor heat exchanger (heat pump heat exchanger)
18 Refrigerant piping 18a Piping section (discharge side pipe line)
18c Piping section (suction side pipe line)
18d Piping section (suction side pipe line)
18e Piping section (third pipe line)
25a Piping section (discharge side pipe line)
25b Piping section (first pipe)
25c Piping section (first pipe)
25d1 Piping section (second pipe)
25d2 Piping section (second pipe)
25e1 Piping section (third pipe line)
25e2 Piping section (third pipe line)
25g Piping section (second pipe)
26a Piping section (second pipe)
26b Piping section (second pipe)
27 Indoor heat exchanger 30 Refrigerant circulation circuit 31 Four-way valve 100 Hot water storage unit 111 Expansion valve (first decompressor)
112 Expansion valve (second pressure reducer)
113 Expansion valve (third decompressor)
121 Two-way valve (first two-way valve)
122 Two-way valve (second two-way valve)
123 Two-way valve 124 Two-way valve 200 Heat pump unit (outdoor unit)
300 Air conditioner unit (indoor unit)
410 Heaton Control Unit 410C Expansion Valve Control Unit (Discharge Temperature Control Unit)
420 Hot Water Storage Control Unit 420B Expansion Valve Control Unit (Diversion Control Unit)
430 Air-conditioner control unit D Branch point E Junction point Nb Target compressor speed during boiling operation (first required heat exchange capacity)
Nh Target compressor speed during heating operation (second required heat exchange capacity)
Nbh Target compressor speed during boiling and heating operation Tair Outside air temperature Tcon Air-conditioner set temperature Tr Indoor temperature

Claims (3)

An indoor heat exchanger as a condenser that performs heat exchange between the refrigerant and room air;
A hot water storage tank for storing hot water,
A water refrigerant heat exchanger as a condenser, comprising a refrigerant passage and a water passage, and performing heat exchange between the refrigerant in the refrigerant passage and water in the water passage;
A heat pump heat exchanger as an evaporator that performs heat exchange between the refrigerant and outside air;
A compressor,
The water passage of the water refrigerant heat exchanger and the hot water storage tank are annularly connected by hot water piping to form a hot water circulation circuit, the indoor heat exchanger, the refrigerant passage of the water refrigerant heat exchanger, the heat pump A heat exchanger and the compressor are connected by refrigerant piping to form a refrigerant circulation circuit, indoor air is heated by the indoor heat exchanger, and water to the hot water storage tank is discharged by the water refrigerant heat exchanger. In a heat pump water heater with a heating function capable of performing heating and heating operations,
The refrigerant pipe is
A discharge side pipe connected to the discharge side of the compressor;
A first pipe that is branched and connected to the discharge side pipe from a predetermined branch point, and the water refrigerant heat exchanger is disposed;
A second pipe that is branched and connected to the discharge side pipe from the branch point, and in which the indoor heat exchanger is disposed;
A junction that joins the first pipeline downstream of the water-refrigerant heat exchanger and the second pipeline downstream of the indoor heat exchanger is connected to the inlet side of the heat pump heat exchanger. 3 pipe lines,
A suction side pipe connecting the outlet side of the heat pump heat exchanger to the suction side of the compressor,
The first pipe line includes a first pressure reducer;
The second conduit includes a second pressure reducer;
The third conduit includes a third pressure reducer;
Flow control for adjusting the valve opening of the first pressure reducer and the second pressure reducer and controlling the flow of the refrigerant that flows separately from the discharge side pipe to the first pipe and the second pipe Means,
A heat pump with a heating function, characterized by comprising discharge temperature control means for adjusting the valve opening of the third decompressor and controlling the refrigerant discharge temperature of the refrigerant discharged from the discharge side of the compressor Water heater. The diversion control means includes:
While the valve opening of the first pressure reducer is fixed, the valve opening of the second pressure reducer is set according to the required heat exchange capability in the indoor heat exchanger and the required heat exchange capability in the water refrigerant heat exchanger. The heat pump water heater with a heating function according to claim 1, wherein a diversion ratio between the first pipeline side and the second pipeline side is controlled by variably controlling. The diversion control means includes:
Depending on the first required heat exchange capability in the water refrigerant heat exchanger and the second required heat exchange capability in the indoor heat exchanger, the valve opening degree of the first decompressor and the second decompressor can be varied. 2. The heat pump water heater with a heating function according to claim 1, wherein the flow dividing ratio between the first pipe line side and the second pipe line side is controlled by controlling.

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