JP7160699B2 - Heat pump water heater with air conditioning function - Google Patents

Description

TECHNICAL FIELD The present invention relates to a heat pump water heater with a cooling and heating function, which has indoor air heating and cooling functions.

Conventionally, in this type of heat pump water heater, as described in Patent Document 1, during cooling operation, the four-way valve is switched to a position where the compressor communicates with the outdoor heat exchanger (heat pump heat exchanger) side, so that the compression Refrigerant is circulated in the order of air conditioner → outdoor heat exchanger → indoor heat exchanger → compressor. In some cases, the refrigerant is circulated in the order of compressor→water-refrigerant heat exchanger→indoor heat exchanger→outdoor heat exchanger→compressor by switching the positions.

JP 2018-63094 A

In the prior art, it is necessary to switch the four-way valve to opposite positions during the cooling operation and during the boiling/cooling operation. Therefore, there is a problem that the room temperature rises due to interruption of operation at the time of switching the four-way valve, resulting in a decrease in cooling sensation.

In order to solve the above problems, claim 1 of the present invention provides a heat pump heat exchanger that can selectively function as a condenser or an evaporator that exchanges heat between a refrigerant and the outside air, and the heat pump heat exchanger A connected compressor, a hot water storage tank that stores hot water, a water-refrigerant heat exchanger as a condenser that exchanges heat between the refrigerant and water, and a condenser that exchanges heat between the refrigerant and indoor air. and an indoor heat exchanger capable of selectively functioning as an evaporator or an evaporator, and the water side 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, In a heat pump water heater with a cooling and heating function in which the heat pump heat exchanger, the compressor, the refrigerant side of the water-refrigerant heat exchanger, and the indoor heat exchanger are connected by refrigerant piping to form a refrigerant circulation circuit, the compression a first switching position in which the discharge side of the compressor is communicated with the heat pump heat exchanger as a condenser and the suction side of the compressor is communicated with the indoor heat exchanger as an evaporator; and the discharge side of the compressor. to the indoor heat exchanger as a condenser and the suction side of the compressor to be communicated to the heat pump heat exchanger as an evaporator; a first pipeline that communicates with the discharge side of the compressor through the four-way valve in the 1 switching position, and the other side of which is connected to the inlet side of the heat pump heat exchanger as a condenser; a second pipeline connecting the outlet side of the heat pump heat exchanger and the inlet side of the indoor heat exchanger as an evaporator; and a third pipeline connected to the outlet side of the indoor heat exchanger as an evaporator on the other side, and one side branched from a first branch point provided in the first pipeline. a fourth pipe having the other side connected to the inlet side of the water-refrigerant heat exchanger as a condenser; and one side branching from a second branch point provided in the second pipe. and a fifth pipeline whose other side is connected to the outlet side of the water-refrigerant heat exchanger as a condenser, and one side of which is branched from a third branch point provided in the first pipeline for evaporation. is connected to the outlet side of the heat pump heat exchanger as a vessel, and the other side is provided by branching from a fourth branch point provided in the third pipeline, and is provided through the four-way valve in the first switching position to the compressor Switching the sixth pipeline and the four-way valve to either the first switching position or the second switching position, which are communicated with the suction side of A four-way valve control means to be replaced, one side of which is branched from a fifth branch point provided in the third pipeline, and the other side of which is connected to the inlet side of the water-refrigerant heat exchanger as a condenser. 7 pipelines, and when the four-way valve is in the second switching position, the third pipeline is connected to the discharge side of the compressor and the inlet side of the indoor heat exchanger as a condenser. , the first pipeline connects the suction side of the compressor and the outlet side of the heat pump heat exchanger as an evaporator, and the second pipeline connects the indoor heat exchanger as a condenser It connects the outlet side of the evaporator and the inlet side of the heat pump heat exchanger as an evaporator .

Further, in claim 2 , a first opening/closing valve provided in the fourth pipeline for opening and closing the fourth pipeline, and a second opening/closing valve provided in the sixth pipeline for opening and closing the sixth pipeline. a valve;
It has

Moreover, in Claim 3 , it is provided in the section between the said 1st branch point and the said 3rd branch point in a said 1st pipeline, and has a 3rd on-off valve which opens and closes the said area.

Further, in claim 4 , a fourth on-off valve capable of closing the indoor heat exchanger side of the third pipeline rather than the fifth branch point, and the second pipeline more than the second branch point. and a fifth on-off valve capable of closing the indoor heat exchanger side.

Further, in claim 5 , the four-way valve control means switches the four-way valve to either the first switching position or the second switching position according to a predetermined operation switching factor.

According to claim 1 of the present invention, cooling (individual) operation can be performed by switching the four-way valve to the first switching position.
That is, by switching to the first switching position, the discharge side of the compressor communicates with the inlet side of the heat pump heat exchanger as a condenser through the first conduit, and the outlet side of the heat pump heat exchanger communicates with the second conduit. It is connected to the inlet side of an indoor heat exchanger as an evaporator via a line, and the outlet side of the indoor heat exchanger communicates with the suction side of the compressor via a third line. As a result, the high-temperature and high-pressure refrigerant gas discharged from the compressor radiates heat to the outside air in the heat pump heat exchanger and condenses into liquid refrigerant, and then evaporates in the indoor heat exchanger to absorb heat from the indoor air and compress it. The cooling operation is realized back to the aircraft.

Further, according to claim 1, a fourth pipeline and a second pipeline are branched and connected from the first pipeline separately from the first pipeline, the second pipeline, and the third pipeline. A fifth pipeline branched from and connected to and a sixth pipeline branched from the first pipeline are provided, and by using these, the four-way valve is set to the first switching position Thus, it is possible to perform a boiling/cooling operation in which the hot water in the hot water storage tank is heated while cooling the indoor space.

That is, through the fourth pipeline branching from the first branch point of the first pipeline, the discharge side of the compressor communicates with the inlet side of a water-refrigerant heat exchanger as a condenser, and the water-refrigerant heat exchange is performed. The outlet side of the vessel is connected via a fifth line to the second branch point of the second line. This second pipe line is connected to the inlet side of the indoor heat exchanger as the evaporator as described above, and the outlet side of the indoor heat exchanger is communicated with the suction side of the compressor via the third pipe line. .
On the other hand, the second pipeline is also connected to the outlet side of the heat pump heat exchanger when functioning as a condenser (in other words, the inlet side of the heat pump heat exchanger as an evaporator). From the third branch point provided in the first pipeline connected to the outlet side of the heat pump heat exchanger as the evaporator (in other words, the inlet side of the heat pump heat exchanger when functioning as a condenser), 6 pipelines are branched and connected, and this 6th pipeline is connected to a 4th branch point provided in the 3rd pipeline, and is communicated with the suction side of the compressor via the 3rd pipeline. It will happen.

With such a connection mode, the high-temperature and high-pressure refrigerant gas discharged from the compressor is introduced into the water-refrigerant heat exchanger through the fourth pipe, and in the water-refrigerant heat exchanger, into the hot water pipe leading to the hot water storage tank. The heat is released and condensed to form a liquid refrigerant, which is then introduced into the second conduit at the second branch point via the fifth conduit. A portion of the liquid refrigerant introduced into the second pipeline is introduced into the indoor heat exchanger from the second branch point, evaporates in the indoor heat exchanger, absorbs heat from the indoor air, and then flows into the third pipeline. while returning to the compressor via, the rest of the liquid refrigerant introduced into the second pipeline is introduced into the heat pump heat exchanger from the second branch point and evaporated in the heat pump heat exchanger to be removed from the outside air. After absorbing the heat, it joins the third pipeline from the third branch point of the first pipeline via the sixth pipeline and returns to the compressor. In this manner, the heating/cooling operation is realized in which the cooling of the indoor space and the heating of the hot water in the hot water storage tank are performed in parallel.

As described above, according to claim 1, both the cooling operation and the boiling/cooling operation can be performed while the four-way valve is switched to the same switching position (first switching position). As a result, unlike the conventional method in which the four-way valve had to be switched to the position opposite to that during the cooling operation during the heating and cooling operation, the suspension of operation during the switching of the four-way valve raises the room temperature and reduces the cooling sensation. You can prevent the decline from occurring.

Further, according to claim 1 , heating (individual) operation can be executed by switching the four-way valve to the second switching position.
That is, by switching to the second switching position, the discharge side of the compressor communicates with the inlet side of the indoor heat exchanger as a condenser through the third pipe line, and the outlet side of the indoor heat exchanger communicates with the second pipe. It is connected to the inlet side of a heat pump heat exchanger as an evaporator via a line, and the outlet side of the heat pump heat exchanger communicates with the suction side of the compressor via a first line. As a result, the high-temperature, high-pressure refrigerant gas discharged from the compressor radiates heat to the indoor air in the indoor heat exchanger and condenses to become liquid refrigerant. , the heating operation can be realized.

On the other hand, the third pipeline is also connected to the inlet side of a water-refrigerant heat exchanger functioning as a condenser via a seventh pipeline branched from the fifth branch point. As described above, the outlet side of this water-refrigerant heat exchanger is connected to the second branch point of the second pipeline via the fifth pipeline, and the evaporator is operated via the second pipeline. will be connected to the inlet side of the heat pump heat exchanger.

With such a connection mode, the high-temperature and high-pressure refrigerant gas discharged from the compressor flows through the route of the third pipe → the indoor heat exchanger → the second pipe → the heat pump heat exchanger to perform the heating. The remainder other than what is performed is diverted to the seventh pipeline branching from the third pipeline, introduced into the water-refrigerant heat exchanger via the seventh pipeline, and stored in the water-refrigerant heat exchanger. Heat is radiated and condensed in the hot water pipe leading to the tank, and the condensed liquid refrigerant is made to join the second pipe line at the second branch point through the fifth pipe line, and can be introduced into the heat pump heat exchanger. . As a result, it is also possible to realize a boiling-up/heating operation in which the heating of the indoor space and the heating of the hot water in the hot water storage tank are performed simultaneously.

As a result, according to claim 1 , both the heating operation and the boiling/heating operation can be performed while the four-way valve is switched to the same switching position (second switching position). As a result, the cooling (individual) operation and the boiling/cooling operation can be performed at the same switching position (first switching position) of the four-way valve, and the heating (independent) operation and the boiling/heating operation can be performed with each other. It can be performed at the switching position (second switching position) of the same four-way valve. In other words, the switching position of the four-way valve is set at least during cooling operation (cooling independent operation, boiling/cooling operation) and at least during heating operation (heating independent operation, boiling/heating operation). ), can be unified in each.

Further, according to claim 2 , for example, in a state in which the four-way valve is in the first switching position, the cooling (individual) operation is executed by closing the first on-off valve and the second on-off valve. By opening the first on-off valve and the second on-off valve, the boiling/cooling operation can be performed. Further, for example, by closing the first on-off valve and the second on-off valve and setting the four-way valve to the second switching position, heating (independent) operation or boiling/heating operation can be performed.

Further, according to claim 3 , by closing the section between the first branch point and the third branch point in the first pipeline by closing the third on-off valve, , compressor discharge side → first pipeline → first branch point → fourth pipeline → . → can be reliably separated from the refrigerant flow of .

Further, according to claim 4 , by closing the fourth on-off valve and the fifth on-off valve, the fifth branch point (fourth on-off valve) ~ third pipeline ~ indoor heat exchanger ~ second pipe A section between the path and the second branch point (fifth on-off valve) is defined as a closed section, and the refrigerant in this section is confined to eliminate refrigerant flow.

Thus, if the four-way valve control means sets the four-way valve to the first switching position, the compressor discharge side→fourth pipeline→water-refrigerant heat exchanger→fifth pipeline→second pipeline→heat pump heat exchanger →Sixth pipeline→Compressor suction side route, boiling-up (single) operation for heating the hot water in the hot water storage tank can be realized. That is, in this case, the heating (individual) operation can be realized at the switching position (first switching position) of the four-way valve common to the cooling (individual) operation and the boiling/cooling operation. As a result, the cooling (individual) operation, the boiling/cooling operation, the boiling (independent) operation, and operation switching between them can be executed without switching the four-way valve.

Alternatively, if the four-way valve control means sets the four-way valve to the second switching position, the compressor discharge side→third pipeline→seventh pipeline→water-refrigerant heat exchanger→fifth pipeline→second pipeline→ A boiling-up (single) operation for heating the hot water in the hot water storage tank can be realized in the route of the heat pump heat exchanger→the first pipe→compressor suction side. That is, in this case, the heating (individual) operation and the boiling/heating operation can be performed at the switching position (second switching position) of the four-way valve common to the boiling operation. As a result, heating (individual) operation, boiling/heating operation, boiling (individual) operation, and operation switching between them can be performed without switching the four-way valve.

As described above, in the present invention, the boiling-up (individual) operation can be performed with the four-way valve set to the first switching position, and the boiling-up (single) operation can be performed with the four-way valve set to the second switching position. can also be done. Therefore, according to claim 5 , the four-way valve control means is set to the first switching position corresponding to the cooling operation or the like or the second switching position corresponding to the heating operation or the like. The four-way valve is controlled according to the switching factor.

Examples of operation switching factors include the outside air temperature detected by appropriate detection means, the water supply temperature to the hot water storage tank, or their average value within a predetermined period (for example, a plurality of days in the past), the cooling operation within a predetermined period, or There is a track record of the operation mode of the heating operation (or a track record of the instruction of the operation mode).

As a result, when the boiling (independent) operation is performed, for example, when the outside temperature or the water supply temperature is relatively low, or when the heating operation has been performed frequently within the predetermined period, etc., the four-way valve The control means considers that the four-way valve should be switched in response to the heating operation or the like, and switches it to the second switching position. As a result, the boiling (single) operation is executed in the second switching position, so even if an instruction to shift to the heating operation or the boiling/heating operation is given thereafter. However, the transition can be performed smoothly while maintaining the same second switching position. As a result, it is possible to reliably prevent a decrease in room temperature (a decrease in feeling of heating) due to suspension of operation such as when the switching position of the four-way valve is changed.

Conversely, when the boiling-up (independent) operation is performed, for example, when the outside air temperature or the water supply temperature is relatively high, or when the cooling operation has been performed frequently within the predetermined period, etc., the four-way valve The control means considers that the four-way valve should be switched in response to the cooling operation or the like, and switches it to the first switching position. As a result, the boiling (single) operation is executed in the state of the first switching position, so even if an instruction to shift to the cooling operation or the boiling/cooling operation is given thereafter. However, the transition can be performed smoothly while maintaining the same first switching position. As a result, it is possible to reliably prevent an increase in room temperature (reduced feeling of cooling) due to suspension of operation, such as when the switching position of the four-way valve is changed.

1 is an external configuration diagram of main units of a heat pump water heater with cooling and heating functions according to one embodiment of the present invention. Circuit configuration diagram of the entire heat pump water heater Functional block diagram of the heat pump control unit Functional configuration diagram of hot water storage controller Functional block diagram of air conditioner control unit Diagram explaining the operation during winter heating operation A diagram showing the control mode of the compressor rotation speed during the boiling operation, the heating operation, and the boiling/heating operation. Diagram explaining operation during heating operation Diagram explaining operation during boiling/heating operation FIG. 4 is a diagram showing a control map when the expansion valve control unit executes flow division control of the expansion valve; Diagram explaining the operation during summer boiling operation Diagram explaining the operation during cooling operation Diagram explaining operation during boiling/cooling operation Diagram for explaining the operation of another example during boiling/cooling operation FIG. 4 is a diagram showing a control map when the expansion valve control unit executes flow division control of the expansion valve; Flowchart diagram showing the control contents of a modified example in which winter boiling operation and summer boiling operation are switched according to the operation switching factor.

An embodiment of the present invention will be described below with reference to FIGS. 1 to 15. FIG.

<External configuration>
FIG. 1 shows the external configuration of main units of the heat pump water heater 1 with cooling and heating functions of the present embodiment. In FIG. 1, the heat pump water heater 1 of the present embodiment includes a hot water storage unit 100 including a hot water storage tank 2 (see FIG. 2, which will be described later), a heat pump unit 300 as an outdoor unit, and an air conditioner unit 200 as an indoor unit. ,have.

<Circuit configuration>
FIG. 2 shows the overall circuit configuration of the heat pump water heater 1 of this embodiment. As shown in FIG. 2, the hot water storage unit 100 has a refrigerant-side flow path 15b and a water-side flow path 15a for circulating the refrigerant, and heat exchanges between the high-temperature and high-pressure refrigerant and the hot water in the hot water storage tank 2. It has a water-refrigerant heat exchanger 15 functioning as a condenser for heating and a boiling pump 19 . That is, the water-side flow path 15 a of the water-refrigerant heat exchanger 15 and the hot water storage tank 2 are annularly connected by a heating supply pipe 5 and a heating return pipe 6 as hot water piping, and hot water is supplied to the hot water storage unit 100 . A heating circulation circuit 4 is formed as a circulation circuit.

A heating feed pipe 5 is connected to the lower portion of the hot water storage tank 2 , and a heating return pipe 6 is connected to the upper portion of the hot water storage tank 2 . The boiling pump 19 is provided in the middle of the heating pipe 5, and circulates hot water from the heating pipe 5 to the heating return pipe 6 through the water-side flow path 15a. Circulate water.

On the side surface of the hot water storage tank 2, a plurality of stored hot water temperature sensors 12 for detecting the temperature of hot water (hot water temperature) in the hot water storage tank 2 and detecting the heating state of the hot water (in other words, hot water storage state) are provided vertically. ing. A water supply pipe 7 for supplying water to the hot water storage tank 2 is also connected to the lower part of the hot water storage tank 2, and a hot water supply pipe 8 for supplying hot water stored in the hot water storage tank 2 is 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 . Further, a mixing valve 10 that mixes the hot water from the hot water supply pipe 8 and the water from the water supply bypass pipe 9 to produce hot water at the hot water supply set temperature; , is provided.

On the other hand, a 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. are set across. The refrigerant circulation circuit 30 includes a heat pump circuit portion 30A arranged inside the heat pump unit 300, a hot water storage circuit portion 30B arranged across the heat pump unit 300 and the hot water storage unit 100, and inside the air conditioner unit 200. and an air conditioner circuit unit 30C.

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

Specifically, one side of the refrigerant pipe 18 communicates with the pipe portion 18c on the discharge side of the compressor 14 and the pipe portion 18c on the discharge side of the compressor 14 during cooling operation (see FIG. 12 described later). and the other side is connected to the compressor 14 side of the outdoor heat exchanger 17 (in other words, the inlet side during the cooling operation, the same applies hereinafter), the piping portion 18d (corresponding to the first pipeline); and a piping portion 18e connected to the side of the outdoor heat exchanger 17 opposite to the compressor 14. The piping portion 18e includes an expansion valve 113 and communicates with a piping portion 25e, which will be described later.

The refrigerant pipe 18 includes a pipe portion 18a on the suction side of the compressor 14 and a pipe portion connected to the pipe portion 18a through the four-way valve 31 during the cooling operation (see FIG. 12 described later). 18b and . The pipe portion 18b communicates with a pipe portion 25m, which will be described later.

<Four-way valve details>
The four-way valve 31 is a valve having four ports, and of the refrigerant pipe 18, each of the two ports for the pipe portions 18b and 18d (constituting the refrigerant main path) is connected to the remaining pipe portions. It switches which of the two ports for 18a and 18c should be connected. The two ports for the piping portions 18a and 18c are connected to each other by a refrigerant subpath composed of the piping portions 18a and 18c arranged in a loop, and the compressor 14 is provided on this refrigerant subpath. ing.

For example, when the four-way valve 31 is switched to the state shown in FIG. The piping portion 18c on the discharge side of is communicated with the piping portion 18d on the outdoor heat exchanger 17 side, and the piping portion 18a on the suction side of the compressor 14 is connected on the indoor heat exchanger 27 side. Communicate with a certain piping portion 18b.
When the four-way valve 31 is switched to the state shown in FIG. 8 described later (=corresponding to the second switching position, hereinafter referred to as "heating position", "switching to heating side", etc.), the piping portion 18c is communicated with the piping portion 18b on the indoor heat exchanger 27 side, and the piping portion 18a is communicated with the piping portion 18d on the outdoor heat exchanger 17 side.

At this time, a two-way valve 125 (corresponding to a third on-off valve) that can be opened and closed is provided in the middle of the piping portion 18 d from the outdoor heat exchanger 17 to the four-way valve 31 . A pipe portion 18f (corresponding to a sixth pipe line) extends from a branch point B (corresponding to a third branch point) located closer to the room heat exchanger 17 than the two-way valve 125 in the pipe portion 18d. The pipe portion 18f is branched and connected to a branch point C (corresponding to a fourth branch point) located in the pipe portion 18b. Further, the pipe portion 18f from the branch point B to the branch point C is provided with a two-way valve 126 (corresponding to a second on-off valve) that can be opened and closed.

<Hot water storage circuit>
The hot water storage circuit section 30</b>B includes a refrigerant pipe 25 that serves as a flow path for the refrigerant, 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 portion 25m connected to the pipe portion 18b at the branch point C, and a branch point E (fifth and a branch point F located on the opposite side of the branch point E in the piping portion 25a, and the side opposite to the piping portion 25a is connected to the water refrigerant heat exchanger. 15 (specifically, the refrigerant-side flow path 15b) connected to the inlet side, and the water-refrigerant heat exchanger 15 (specifically, the refrigerant-side flow path 15b) connected to the outlet side. and a piping portion 25c (corresponding to a fifth pipeline). The piping portion 25b has a two-way valve 121 that can be opened and closed, and the piping portion 25c has an expansion valve 111 with a fully closed function.

The refrigerant pipe 25 includes a pipe portion 25h connected to the branch point F of the pipe portion 25a and a branch point G located on the opposite side of the branch point F in the pipe portion 25h. and a pipe portion 25d connected to the . The side of the pipe portion 25d opposite to the pipe portion 25h communicates with a communication pipe line 104 that connects the heat pump unit 300 and the air conditioner unit 200 at a connection port 95a serving as an outlet to the outside of the heat pump unit 300 .

Further, the refrigerant pipe 25 is connected to a branch point D located on the anti-water refrigerant heat exchanger 15 side of the pipe portion 25c, and the pipe portion 25e that communicates with the pipe portion 18e on the side opposite to the pipe portion 25c; A pipe portion 25f connected to the branch point G, a pipe portion 25i connecting the branch point H and the branch point E located on the opposite side of the branch point G in the pipe portion 25f, and the pipe portion 18d. Among them, a piping portion 25j connected to a branch point A located on the side of the four-way valve 31 from the two-way valve 125, and a branch point J and the branch point H located on the opposite side of the branch point A in the piping portion 25j. and a piping portion 25k that connects the branch point I and the branch point J located closer to the water-refrigerant heat exchanger 15 than the two-way valve 121 in the piping portion 25b, contains. The piping section 25h has an expansion valve 114 with a fully closed function, the piping section 25i has a two-way valve 122 (equivalent to a fourth on-off valve) that can be opened and closed, and the piping section 25k can be opened and closed. A two-way valve 124 is provided, and the piping portion 25l is provided with a two-way valve 123 (corresponding to a first on-off valve) that can be opened and closed.

Further, the refrigerant pipe 25 is connected to the branch point D located on the side opposite to the water refrigerant heat exchanger 15 of the pipe portion 25c in the same manner as the pipe portion 25e, and is a connection port serving as an outlet to the outside of the heat pump unit 300. 95 b includes a pipe portion 25 g that communicates with the communication pipe line 103 that connects the heat pump unit 300 and the air conditioner unit 200 . The piping portion 25g is provided with an expansion valve 112 (corresponding to a fifth on-off valve) with a fully closed function.

The compressor 14, the four-way valve 31, the outdoor heat exchanger 17, the outdoor fan 67, the two-way valves 122, 123, 124, 125, 126, the expansion valves 111, 112, 113, 114, etc. 300 housing (see FIG. 1). Note that the expansion valve 112 may be provided in a pipe portion 26b (that is, inside the housing of the air conditioner unit 200), which will be described later.
The two-way valve 121, the water-refrigerant heat exchanger 15, the hot water storage tank 2, and the like are included in the housing of the hot water storage unit 100 (see FIG. 1).

<Air conditioner circuit part>
The air conditioner circuit unit 30C includes a refrigerant pipe 26 that serves as a flow path for the refrigerant, and selectively functions as a condenser or an evaporator (details will be described later) by heat exchange between the refrigerant and indoor air. An exchanger 27 is connected to the refrigerant pipe 26 . The indoor heat exchanger 27 is provided with an indoor fan 77 for passing the indoor air through the indoor heat exchanger 27 .

Specifically, the refrigerant pipe 26 communicates with the communication pipe line 104 at a connection port 76a serving as an outlet to the outside of the air conditioner unit 200, and the connection port 76a of the indoor heat exchanger 27 is connected to the non-communication pipe line 104 side. side (in other words, the inlet side during heating operation, etc.; the same applies hereinafter; see FIG. 8 and the like, which will be described later). In addition, the side of the anti-communication pipe line 103 is connected to the side of the connection port 76b of the indoor heat exchanger 27 (in other words, the outlet side during heating operation, etc., the same applies hereinafter, see FIG. 8 etc. described later). , contains

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

In the circuit configuration described above, the piping portion 18e, the piping portion 25e, the piping portion 25g, the communicating pipe line 103, and the piping portion 26b correspond to the second pipe line described in each claim. The pipe portion 18b, the pipe portion 25m, the pipe portion 25i, the pipe portion 25f, the pipe portion 25d, the communication pipe line 104, and the pipe portion 26a correspond to the third pipe line. Further, the piping portion 25j and the piping portion 25l correspond to a fourth piping line, and the piping portions 25a and 25b correspond to a seventh piping line.

<Various sensors>
For example, R32 refrigerant is used as a refrigerant in the refrigerant circulation circuit 30 to form a heat pump cycle. Note that the refrigerant may be an HFC refrigerant, an HFO refrigerant, or a carbon dioxide refrigerant. In the refrigerant pipe 18 of the heat pump circuit portion 30A, the pipe portion 18c is provided with a discharge temperature sensor 32 for detecting the refrigerant discharge temperature Tout discharged from the compressor 14. A suction temperature sensor 20 is provided to detect a refrigerant suction temperature Tin of refrigerant sucked into the compressor 14 . 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 outdoor heat exchanger 17 has a heat pump heat exchanger temperature Tex (acting as an evaporator). A heat exchanger temperature sensor 35 is provided for detecting the temperature of the evaporating refrigerant (at the time of heating). The detection results of these sensors 32, 20, 22, and 35 are input to the heat pump control section 410 provided in the heat pump unit 300, and further provided to the hot water storage control section 420 provided in the hot water storage unit 100 and the air conditioner unit 200 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 32, 20, 22).

Further, in the refrigerant pipe 25 of the hot water storage circuit portion 30B, the pipe portion 25c is provided with an outflow temperature sensor 21 for detecting a refrigerant outflow temperature T2 flowing out from the refrigerant-side flow path 15b toward the expansion valve 111. It is The water-refrigerant heat exchanger 15 is provided with a condensation temperature sensor 33 for detecting the refrigerant condensation temperature when the refrigerant is condensed in the refrigerant-side passage 15b. Further, the heating supply pipe 5 is provided with an incoming water temperature sensor 23 for detecting an incoming water temperature T1 (inlet temperature of hot water) 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 15 a toward the hot water storage tank 2 .
The detection results of these sensors 21, 33, 23, and 24 are input to the hot water storage control section 420 provided in the hot water storage unit 100, and further to the heat pump control section 410 provided in the heat pump unit 300 and the air conditioner unit 200 as appropriate. It is also input to the provided air conditioner control unit 430 (it may be received via the hot water storage control unit 420, or may be received directly from the sensors 21, 33, 23, 24).

Further, regarding 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-conditioned space. A heat exchanger temperature sensor 36 is provided for detecting the indoor heat exchanger temperature Tev (evaporated refrigerant temperature when acting as an evaporator). The detection results of these sensors 34 and 36 are input to the air conditioner control section 430 provided in the air conditioner unit 200, and furthermore, the heat pump control section 410 provided in the heat pump unit 300 and the hot water storage unit 100 provided in the hot water storage unit 100 are input as appropriate. It is also input to the control unit 420 (it may be received via the air conditioner control unit 430 or may be received directly from the sensor 34).

The hot water storage controller 420 of the hot water storage unit 100, the heat pump controller 410 of the heat pump unit 300, and the air conditioner controller 430 of the air conditioner unit 200 are connected so as to be able to communicate 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 four-way valve 31, the two-way valves 121, 122, 123, 124, 125, 126, and the expansion valves 111, 112, 113, 114 are controlled to open and close and to switch paths through which the refrigerant flows. A heating operation for heating and boiling the hot water in the hot water storage tank 2, a cooling operation for indoor cooling of the air-conditioned space, a heating operation for indoor heating of the air-conditioned space, the boiling and the cooling. A boiling-up/cooling operation in which the heating is performed in parallel, a boiling-up/heating operation in which the heating and the heating are performed in parallel, and the like can be selectively executed.

<Remote control>
At this time, the air conditioner unit 200 can be operated by an appropriate operating section 60 such as a remote controller (hereinafter simply referred to as "remote controller 60"). That is, the remote controller 60 is connected to, for example, the air conditioner control unit 430 so that information can be transmitted and received. It is possible to instruct which operation of the operation is to be performed. Regarding the boiling/cooling operation (or boiling/heating operation), when the user instructs the cooling operation (or heating operation) via the remote control 60, the hot water storage state (unheated water) in the hot water storage tank 2 etc.), it is automatically switched to boiling/cooling operation (or boiling/heating operation) as appropriate. Furthermore, by appropriately operating the remote controller 60, a boiling mode during the boiling operation (for example, a strong boiling mode, a normal boiling mode, etc.) or an air conditioner operating mode during the cooling operation or heating operation (for example, a strong boiling mode) 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 section 430 provided in the air conditioner unit 200, and furthermore, as appropriate, the heat pump control section 410 provided in the heat pump unit 300 and the hot water storage unit 100 are provided. It is also input to hot water storage control unit 420 (it may be received via air conditioner control unit 430 or may be received directly from remote controller 60).

<Heapon control unit>
Next, the heat pump control section 410 provided in the heat pump unit 300 will be described. Although not shown in detail, the heat pump control unit 410 includes a storage unit that stores various data and programs, and a control unit that performs arithmetic and control processing. A functional configuration of the heat pump 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 (corresponding to four-way valve control means), a compressor control unit 410B, an expansion valve control unit 410C, an outdoor fan control unit 410D, and a two-way valve control unit 410E.

The four-way valve control unit 410A receives an operation instruction (boiling operation, cooling operation, heating operation, etc.) instructed by the remote control 60 and the stored hot water detected by the stored hot water temperature sensor 12. temperature is entered. The four-way valve control unit 410A actually controls the heat pump water heater 1 in what kind of operation mode (boiling operation, cooling operation, boiling-up/cooling operation, heating operation, boiling-up/heating operation, etc.), and the corresponding operation information is sent to the compressor control unit 410B, the expansion valve control unit 410C, and the outdoor fan control unit 410D. , the two-way valve control unit 410E, the hot water storage control unit 420, and the air conditioner control unit 430. The four-way valve control unit 410A also outputs an open/close signal corresponding to the determined operating mode to the four-way valve 31 to switch the four-way valve 31 (details of control will be described later).

The outside air temperature Tair detected by the outside air temperature sensor 22, the inside temperature Tr detected by the inside temperature sensor 34, and the air conditioner set temperature Tcon set by the remote controller 60 are stored in the compressor control unit 410B. and the boiling mode are input (in addition to direct input, the above-mentioned indirect input is also included; the same applies hereinafter). The compressor control unit 410B receives input from the four-way valve control unit 410A as described above (boiling operation, cooling operation, boiling/cooling operation, heating operation, and boiling/heating operation). The number of revolutions of the compressor 14 is controlled based on at least one of the input temperature and setting according to the operation information (details of control content will be described later). Note that the rotational speed (control value) of the compressor 14 at this time is also output to an expansion valve control section 410C, which will be described later.

The expansion valve control unit 410C stores the air conditioner operation mode set by the remote controller 60, the refrigerant discharge temperature Tout detected by the discharge temperature sensor 32, and the refrigerant outflow temperature detected by the outflow temperature sensor 21. T2, the outside air temperature Tair detected by the outside air temperature sensor 22, the refrigerant intake temperature Tin detected by the intake temperature sensor 20, and the heat exchanger heat exchanger temperature Tex detected by the heat exchanger temperature sensor 35 and the indoor heat exchanger temperature Tev detected by the heat exchanger temperature sensor 36 are input. The expansion valve control unit 410C adjusts the opening degrees of the expansion valves 111, 112, 113, and 114 based on at least one of the input temperatures in accordance with the operation information from the four-way valve control unit 410A. control (details of control will be described later).

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 are input to the outdoor fan control unit 410D. The outdoor fan control unit 410D controls the rotation speed of the outdoor fan 67 based on the outside air temperature Tair and the operation mode according to the operation information from the four-way valve control unit 410A (details of control will be described later). .

The operation information from the four-way valve control section 410A is input to the two-way valve control section 410E. The two-way valve control unit 410E controls opening and closing operations of the two-way valves 122, 123, 124, 125, and 126 based on the operation information (details of control will be described later).

Note that the determination of the operation mode may be performed by the hot water storage control section 420 or the air conditioner control section 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 is controlled according to the input operation information. , a compressor control unit 410B, an expansion valve control unit 410C, an outdoor fan control unit 410D, and a two-way valve control unit 410E perform various controls.

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

As shown in FIG. 4, the hot water storage controller 420 functionally includes a pump controller 420A and a two-way valve controller 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 receives input from the heat pump control unit 410 as described above (any operation such as boiling operation, cooling operation, boiling/cooling operation, heating operation, and boiling/heating operation is performed. The number of revolutions of the boiling pump 19 is controlled based on the input boiling temperature Tb according to the operation information (details of control content 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 valve 121 based on the operation information (details of control will be described later).

Note that the operation mode may be determined in the hot water storage control section 420 (for example, the two-way valve control section 420C) or the air conditioner control section 430 in the same manner as described above. In this case, the pump control section 420A and the two-way valve control section 420C perform various controls according to the operating information corresponding to the operating mode determined by the two-way valve control section 420C and the air conditioner control section 430. FIG.

<Air conditioner controller>
Next, the air conditioner control section 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, similarly to the heat pump control unit 410 and the hot water storage control unit 420, and the functional configuration thereof will be described with reference to FIG.

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

The indoor fan controller 430A receives the operation information from the heat pump controller 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. be done. The indoor fan control unit 430A controls the rotation speed of the indoor fan 77 based on the indoor temperature Tr and the air conditioner set temperature Tcon in accordance with the operation information from the heat pump control unit 410 (details of control will be described later). ).

Note that the operation mode may be determined in the air conditioner control unit 430 or the hot water storage control unit 420 in the same manner as described above. 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. FIG.

As described above, the heat pump water heater 1 of the present embodiment can selectively execute various types of operations such as boiling operation, cooling operation, heating operation, boiling/cooling operation, and boiling/heating operation. can. Details of each operation will be described below.

<Winter heating operation>
First, the boiling-up operation will be explained. In addition, in the present embodiment, for example, different modes of boiling-up operation can be performed in winter and summer (details will be described later). (referred to as upward operation) will be described with reference to FIG.

During the winter boiling operation shown in FIG. 6, the four-way valve control section 410A causes the four-way valve 31 to connect the piping section 18c to the piping section 18b and connect the piping section 18a to the piping section 18d. It is switched to the communication position (the heating position). The two-way valve control units 410E and 420C control the two-way valve 121 to be fully open, the two-way valve 123 to be fully closed, the two-way valve 122 to be fully closed, the two-way valve 125 to be fully open, and the two-way valve 126 to be fully opened. is fully closed, and the two-way valve 124 is switched to the fully closed state. Further, the expansion valve control unit 410C controls the expansion valve 112 to be fully closed, the expansion valve 114 to be fully closed, the expansion valve 113 to be open (specifically, ΔH control, which will be described later), and the expansion valve 113 to be fully closed. Valve 111 is controlled to be fully open.

As a result, the piping section 18c on the discharge side of the compressor 14→piping section 18b→piping section 25m→piping section 25a→piping section 25b (two-way valve 121)→flow path 15b on the refrigerant side of the water-refrigerant heat exchanger 15→ Pipe portion 25c (expansion valve 111)→Pipe portion 25e→Pipe portion 18e (expansion valve 113)→Outdoor heat exchanger 17→Pipe portion 18d (two-way valve 125)→Refrigerant in pipe portion 18a on the suction side of compressor 14 A path is formed. As a result, after the gaseous refrigerant sucked at low temperature and low pressure is compressed by the compressor 14 to become a high temperature and high pressure gas, the refrigerant side flow of the water-refrigerant heat exchanger 15 functioning as a condenser In the passage 15b, the water exchanges heat with the water flowing through the passage 15a on the water side, releases heat to the water, heats the water, and changes into a high-pressure liquid. The liquid refrigerant passes through the fully open expansion valve 111 and is decompressed by the expansion valve 113 to become a low-temperature, low-pressure liquid, which is easily evaporated. It absorbs heat by exchanging heat with the outside air, evaporating and changing to gas, and returns 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 supply pipe 5 connected to the lower part of the hot water storage tank 2 receives heat from the condensed refrigerant in the water-side flow path 15a of the water-refrigerant heat exchanger 15. After being heated to a high temperature, the hot water is returned into the hot water storage tank 2 through a heating return pipe 6 connected to the top of the hot water storage tank 2, so that high temperature water (heated water) is sequentially stored in the hot water storage tank 2 in a layered manner. be.

At this time, the expansion valve 112, the expansion valve 114, the two-way valve 122, and the two-way valve 124 are controlled to be fully closed, so that the indoor heat exchanger 27 and the indoor heat exchanger 27 Inside the piping portion 25i, the piping portion 25f, the piping portion 25d, the communication pipeline 104, the piping portion 26a, the piping portion 26b, the communication pipeline 103, etc., which communicate to the side, the A state in which the refrigerant is enclosed is reached (see the lower left table in FIG. 6).

In the above operation, the target rotation speed of the compressor 14 (hereinafter referred to as “target rotation speed Nb” for boiling operation) is controlled by the compressor control unit 410B based on the outside air temperature Tair. It is determined. That is, for example, as shown by the right-down characteristic line in FIG. 7A, when the outside air temperature Tair is low, the target rotation speed Nb is controlled to be large, and when the outside air temperature Tair is high, the target rotation speed Nb is small. controlled to be The outdoor fan rotation speed N2 of the outdoor fan 67 is determined based on the outside air temperature Tair under the control of the outdoor fan control section 410D. That is, when the outside air temperature Tair is low, the fan rotation speed is controlled to increase, and when the outside air temperature Tair is high, the fan rotation speed is controlled to decrease (not shown). Here, the target rotational speed Nb of the compressor 14 and the outdoor fan rotational speed N2 are determined so as to achieve a predetermined constant boiling capacity regardless of whether the outside air temperature Tair is high or low. .

Returning to FIG. 6, the rotation speed of the boiling pump 19 is feedback-controlled by the control of the pump control section 420A so that the boiling temperature Tb becomes a predetermined target temperature. That is, when the boiling temperature Tb is lower than the target temperature, the pump rotation speed is controlled to decrease (the flow rate decreases), and when the boiling temperature Tb is higher than the target temperature, the pump rotation speed increases (the flow rate decreases). increased). The indoor fan 77 is stopped from rotating under the control of the indoor fan controller 430A.

The degree of opening of the expansion valve 113 is variably controlled by the expansion valve control section 410C according to the operating state of the winter boiling operation. Specifically, the degree of opening of the expansion valve 113 is changed 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. Feedback control (ΔH control). That is, the expansion valve control unit 410C controls the opening of the expansion valve 113 to close when ΔH<ΔHm, and to open the expansion valve 113 when ΔH>ΔHm. When ΔH=ΔHm, the opening of the expansion valve 113 is maintained as it is.
Alternatively, instead of this ΔH control, feedback control of the degree of opening of the expansion valve 113 may be performed 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 of the expansion valve 113 to close when the refrigerant discharge temperature Tout is too low, and opens the expansion valve 113 when the refrigerant discharge temperature Tout is too high. Control direction.

<Heating operation>
Next, the heating operation will be described with reference to FIG. During the heating operation shown in FIG. 8, the four-way valve control section 410A switches the four-way valve 31 to the heating position as in the winter heating operation. The two-way valve control units 410E and 420C control the two-way valve 121 to be fully closed, the two-way valve 123 to be fully closed, the two-way valve 122 to be fully open, the two-way valve 125 to be fully open, and the two-way valve 126 to be fully closed. is fully closed, and the two-way valve 124 is switched to the fully closed state. Further, the expansion valve control unit 410C controls the expansion valve 112 in the fully open state, the expansion valve 114 in the fully closed state, the expansion valve 113 in the open state (specifically, discharge control similar to that described above is performed), and the expansion valve 113 is opened. The valve 111 is controlled to be fully closed.

As a result, the piping portion 18c on the discharge side of the compressor 14→piping portion 18b→piping portion 25m→piping portion 25i (two-way valve 122)→piping portion 25f→piping portion 25d→communication pipe line 104→piping portion 26a→indoor Heat exchanger 27→pipe portion 26b→communication pipe line 103→pipe portion 25g (expansion valve 112)→pipe portion 25e→pipe portion 18e (expansion valve 113)→outdoor heat exchanger 17→pipe portion 18d (two-way valve 125 ) → A refrigerant path of the piping portion 18a on the suction side of the compressor 14 is formed. As a result, the gaseous refrigerant drawn in at low temperature and low pressure is compressed by the compressor 14 to become a high temperature and high pressure gas, and then heat exchanged with the indoor air in the indoor heat exchanger 27 functioning as a condenser. As the air moves, heat is released, and the space to be air-conditioned is heated while changing into a high-pressure liquid. The liquid refrigerant passes through the fully open expansion valve 112 and is decompressed by the expansion valve 113 to become a low-temperature, low-pressure liquid, which is easily evaporated. It absorbs heat by exchanging heat with the outside air, evaporating and changing to gas, and returns to the compressor 14 again as a low-temperature, low-pressure gas.

At this time, the expansion valve 111, the two-way valve 121, and the two-way valve 123 are controlled to be fully closed, thereby communicating with the water-refrigerant heat exchanger 15 and the water-refrigerant heat exchanger 15 side. The refrigerant is confined inside the piping portion 25l, the piping portion 25b, and the portion of the piping portion 25c on the side of the water-refrigerant heat exchanger 15 (lower left table in FIG. 8). reference).

In the above operation, the target rotation speed of the compressor 14 (hereinafter referred to as “target rotation speed Nh” for heating operation) is controlled by the compressor control unit 410B so that the air conditioner set temperature Tcon minus the above When the indoor temperature Tr (=temperature difference ΔT, hereinafter simply referred to as “temperature difference ΔT”) is large, the temperature difference ΔT (=Tcon-Tr) is adjusted so that the target rotation speed becomes large. 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 It is divided into four categories of ≦10 [° C.] and 10<T [° C.].

Then, when the temperature difference ΔT is within the range of ΔT≦2 [° C.], which is the smallest among the four categories, the compressor control unit 410B sets the target rotation speed Nh of the compressor 14 to 20 [rps]. ]. Further, when the temperature difference ΔT is in the range of 2<ΔT≦5 [° C.], which is the second smallest among the four categories, the compressor control unit 410B controls the target rotation speed Nh of the compressor 14 is controlled to be 30 [rps]. Further, when the temperature difference ΔT is in the range of 5<ΔT≦10 [° C.], which is the second largest among the four categories, the compressor control unit 410B controls the target rotation speed Nh of the compressor 14 is controlled to be 40 [rps]. Then, when the temperature difference ΔT is within the largest range of 10<ΔT [° C.] among the four categories, the compressor control unit 410B sets the target rotation speed Nh of the compressor 14 to 50 [rps ].

Returning to FIG. 8, the rotation speed of the outdoor fan 67 is determined based on the outside air temperature Tair and the air conditioner operation mode under the control of the outdoor fan control section 410D. That is, in each of a plurality of prepared air conditioner operation modes (for example, strong mode, normal mode, power saving mode, etc.), when the outside temperature Tair is low, the fan rotation speed is controlled to increase, and when the outside temperature Tair is high, The fan rotation speed is controlled to be small.

The rotation speed of the indoor fan 77 is determined based on the difference between the indoor temperature Tr and the air conditioner set temperature Tcon under the control of the indoor fan control section 430A. That is, when the value of Tcon-Tr is large, the fan speed is controlled to increase, and when the value of Tcon-Tr is small, the fan speed is controlled to decrease. The boiling pump 19 is stopped from rotating under the control of the pump control section 420A.

The degree of opening of the expansion valve 113 is variably controlled by the expansion valve control section 410C according to the operating state of the heating operation. Specifically, the degree of opening of the expansion valve 113 is feedback-controlled so that the refrigerant discharge temperature Tout becomes a predetermined constant value (discharge control similar to that described above). In this case, the expansion valve control unit 410C controls the opening of the expansion valve 113 to close when the refrigerant discharge temperature Tout is too low, and opens the expansion valve 113 when the refrigerant discharge temperature Tout is too high. Control direction. Instead of the discharge control, 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 exchanger temperature Tex becomes a predetermined constant value. (SH control). In this case, the expansion valve control unit 410C controls the opening of the expansion valve 113 in the closing direction when the Tin-Tex is too small, and in the opening direction of the expansion valve 113 when the Tin-Tex is too large. Control.

<Boiling/heating operation>
Next, the boiling/heating operation will be described with reference to FIG. The four-way valve control section 410A switches the four-way valve 31 to the heating position even during the boiling/heating operation shown in FIG. The two-way valve control units 410E and 420C control the two-way valve 121 to be fully open, the two-way valve 123 to be fully closed, the two-way valve 122 to be fully closed, the two-way valve 125 to be fully open, and the two-way valve 126 to be fully opened. is fully closed, and the two-way valve 124 is switched to the fully closed state. Further, the expansion valve control unit 410C controls the expansion valve 112 to be in a fully open state, the expansion valves 114 and 111 to be in an open state (specifically, branch flow control described later), and the expansion valve 113 to be in an open state (specifically, ΔH control similar to that described above is performed).

As a result, the refrigerant path passes through the piping portion 18c on the discharge side of the compressor 14→the piping portion 18b→the piping portion 25m→the piping portion 25a, and is divided into two at the branch point F. valve 121)→flow path 15b on the refrigerant side of the water-refrigerant heat exchanger 15→pipe portion 25c (expansion valve 111) to reach the branch point D, and the other is the pipe portion 25h (expansion valve 114)→pipe portion 25d. →Communication pipeline 104→Pipe part 26a→Indoor heat exchanger 27→Pipe part 26b→Communication pipeline 103→Pipe part 25g (expansion valve 112) to the branch point D. These two routes merge at the branch point D, and the subsequent route is the branch point D→pipe section 25e→pipe section 18e (expansion valve 113)→outdoor heat exchanger 17→pipe section 18d (two-way valve 125). → It becomes the piping portion 18 a on the suction side of the compressor 14 .

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

In the operation described above, the rotation speed of the compressor 14 is controlled by the compressor control unit 410B, and the target rotation speed Nb (see FIG. ) and the target rotation speed Nh (see FIG. 7(b)) during the heating operation determined based on the temperature difference ΔT (=air conditioner set temperature Tcon−indoor temperature Tr). It is controlled so as to reach the target rotation speed Nbh (=Nb+Nh). That is, as shown in FIG. 7C, in this example, the temperature difference ΔT increases, the characteristic line to be used is switched step by step so that the characteristic line is closer to the high rotation speed side.

Specifically, as shown in FIG. 7(c), when the temperature difference ΔT is within the range of ΔT≦2 [° C.], the compressor control unit 410B reduces the target rotation speed Nbh to , 20 [rps] shown in FIG. c) Control is performed so as to obtain the characteristics indicated by the dashed line in (that is, Nbh=Nb+20). Further, when the temperature difference ΔT is in the range of 2<ΔT≦5 [° C.], the compressor control unit 410B sets the target rotation speed Nbh to the target during the boiling operation indicated by the solid line. Control is performed so that the characteristic shown by the dashed line in FIG. 7(c) is obtained by adding 30 [rps] shown in FIG. 7(b) to the rotational speed Nb (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 rotation speed Nbh to the target during the boiling operation indicated by the solid line. Control is performed so that the characteristic shown by the dotted line in FIG. 7(c) is obtained by adding 40 [rps] shown in FIG. 7(b) to the rotational speed Nb (that is, Nbh=Nb+40). Furthermore, when the temperature difference ΔT is in the range of 10<ΔT [° C.], the compressor control unit 410B sets the target rotation speed Nbh to the target rotation speed during the boiling operation indicated by the solid line. Control is performed so that Nb is added with 50 [rps] shown in FIG. 7(b) to obtain the characteristic indicated by the chain double-dashed line in FIG. 7(c) (that is, Nbh=Nb+50).

Returning to FIG. 9, the number of rotations of the outdoor fan 67 is controlled by the outdoor fan control unit 410D, similarly to during the heating operation, based on the outside air temperature Tair and the air conditioner operation mode in each air conditioner operation mode. When the Tair is low, the fan rotation speed is controlled to increase, and when the outside air temperature Tair is high, the fan rotation speed is controlled to decrease.

In addition, the pump control unit 420A controls the rotation speed of the boiling pump 19 to reduce the pump rotation speed when the boiling temperature Tb is lower than the target temperature, as in the winter boiling operation. is higher than the target temperature, the pump speed is controlled to increase. Further, the number of revolutions 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 case of the heating operation. When the value of Tcon-Tr is small, the fan rotation speed is controlled to decrease so that the fan rotation speed increases.

The degree of opening of the expansion valve 113 is variably controlled by the expansion valve control unit 410C according to the operating state of the boiling/heating operation. The temperature difference ΔH=Tout−T2 from the refrigerant outflow temperature T2 is feedback-controlled at a predetermined cycle so that it becomes a predetermined target temperature difference ΔHm (the aforementioned ΔH control).

Further, the opening degrees of the expansion valves 111 and 114 are controlled by the expansion valve control unit 410C to distribute and supply the refrigerant to the water-refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side at a desired ratio (split flow ratio). , is variably controlled by the shunt control. Details of the control contents of this flow division control will be described with reference to FIGS. 10(a) and 10(b).

FIG. 10(a) shows an example of a control map of the opening degree control of the expansion valve 111 executed by the expansion valve control section 410C. In the maps shown in FIGS. 10( a ) and 10 ( b ), the vertical axis indicates the required boiling capacity (in this example, the target rotation speed Nb during boiling as a corresponding index) in the downward increasing direction, and the horizontal axis The value of the target opening in each state (for example, when the fully closed state is "0 ” represents the relative value at which the fully open state is “500”).

As shown in FIG. 10(a), for example, when the required heating capacity during boiling/heating operation is at the minimum level and the required boiling capacity is also at the minimum level, the target opening of the expansion valve 111 is The opening is controlled to be "250" (for example, an opening that is just between fully open and fully closed). If the required boiling capacity is increased by one rank while the required heating capacity remains at the minimum level, the target opening of the expansion valve 111 is controlled to a slightly larger opening of "300", and furthermore, the required boiling capacity is increased. When the required boiling capacity is increased by one rank, the target opening of the expansion valve 111 is controlled to be a slightly larger opening of "350". The opening is controlled to be a large opening of "400", and when the required boiling capacity is increased by one rank, the target opening of the expansion valve 111 becomes a slightly larger opening of "450" (a state close to a fully open state). controlled as As the degree of opening of the expansion valve 111 gradually increases in this way, the split flow ratio to the water-refrigerant heat exchanger 15 side in the split flow to the water-refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side increases. controlled as

Similarly, when the required heating capacity is one rank higher than the minimum level and the required boiling capacity is at the minimum level, the target opening of the expansion valve 111 is smaller than the opening "250". It is controlled to be "200". As a result, the split flow ratio to the indoor heat exchanger 27 side in the split flow is slightly increased (compared to the case where the opening degree is "250"). If the required boiling-up capacity is increased by one rank in this state, the target opening of the expansion valve 111 is controlled to be a slightly larger opening of "250", and thereafter the required boiling-up capacity is increased by one rank. As the temperature increases, the target opening of the expansion valve 111 is controlled to gradually increase to "300", "350", and "400", and the split flow ratio to the water-refrigerant heat exchanger 15 side increases.

Furthermore, in the same manner as described above, when the required heating capacity is two ranks higher than the minimum level and the required boiling capacity is at the minimum level, the target opening of the expansion valve 111 is further than the opening "200". It is controlled to have a small opening of "150". As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "200"). In this state, the target opening of the expansion valve 111 is controlled to gradually increase to "200," "250," "300," and "350" as the required boiling-up capacity increases by one rank. , the split ratio to the water-refrigerant heat exchanger 15 increases.

Furthermore, in the same manner as described above, when the required boiling capacity is at the minimum level while the required heating capacity is three ranks higher than the minimum level, the target opening of the expansion valve 111 is further than the opening "150". It is controlled to have a small opening of "100". As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "150"). In this state, the target opening of the expansion valve 111 is controlled to gradually increase to "150," "200," "250," and "300" as the required boiling-up capacity increases by one rank. , the split ratio to the water-refrigerant heat exchanger 15 increases.

Furthermore, 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 target opening of the expansion valve 111 is 50, which is smaller than the opening of 100. ” is controlled. As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "100"). In this state, the target opening of the expansion valve 111 is controlled to gradually increase to "100", "150", "200", and "250" as the required boiling-up capacity increases by one rank, The split ratio to the water-refrigerant heat exchanger 15 side increases.

FIG. 10(b) shows an example of a control map for controlling the degree of opening of the expansion valve 114 executed by the expansion valve control section 410C. In the map shown in FIG. 10(b), in the same manner as described above, the vertical axis indicates the required boiling capacity (target rotation speed Nb during boiling), and the horizontal axis indicates the required heating capacity (target rotation speed Nh during heating). Represents for direction.

As shown in FIG. 10(b), for example, when the required heating capacity during boiling/heating operation is at a minimum level and the required boiling capacity is also at a minimum level, the target opening of the expansion valve 114 is The opening is controlled to be "250". If the required boiling capacity is increased by one rank while the required heating capacity remains at the minimum level, the target opening of the expansion valve 114 is controlled to a slightly smaller opening of "200", and furthermore, the required boiling capacity is increased. When the required boiling capacity is increased by one rank, the target opening of the expansion valve 114 is controlled to be a slightly smaller opening of "150". The opening is controlled to be a small opening of "100", and when the required boiling capacity is further increased by one rank, the target opening of the expansion valve 114 is controlled to be a slightly larger opening of "50". As the degree of opening of the expansion valve 114 gradually decreases in this way, the split flow ratio to the water-refrigerant heat exchanger 15 side in the split flow to the water-refrigerant heat exchanger 15 side and the indoor heat exchanger 27 side increases. controlled as

Similarly, when the required heating capacity is one rank higher than the minimum level and the required boiling capacity is at the minimum level, the target opening of the expansion valve 114 is greater than the opening "250". It is controlled to be "300". As a result, the split flow ratio to the indoor heat exchanger 27 side in the split flow is slightly increased (compared to the case where the opening degree is "250"). If the required boiling-up capacity is increased by one rank in this state, the target opening of the expansion valve 114 is controlled to be a slightly smaller opening of "250", and then the required boiling-up capacity is increased by one rank. As the temperature increases, the target opening of the expansion valve 114 is controlled to gradually decrease to "200", "150", and "100", and the split flow ratio to the water-refrigerant heat exchanger 15 side increases.

Further, in the same manner as described above, when the required heating capacity is two ranks higher than the minimum level and the required boiling capacity is at the minimum level, the target opening of the expansion valve 114 is further than the opening "300". It is controlled to have a large opening of "350". As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "300"). In this state, the target opening of the expansion valve 114 is controlled to gradually decrease to "300," "250," "200," and "150" as the required boiling-up capability increases by one rank. , the split ratio to the water-refrigerant heat exchanger 15 increases.

Furthermore, in the same manner as described above, when the required boiling capacity is at the minimum level while the required heating capacity is three ranks higher than the minimum level, the target opening of the expansion valve 114 is further than the opening 350. It is controlled to have a large opening of "400". As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the opening degree "350"). In this state, the target opening of the expansion valve 114 is controlled to gradually decrease to "350," "300," "250," and "200" as the required boiling-up capacity increases by one rank. , the split ratio to the water-refrigerant heat exchanger 15 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 target opening of the expansion valve 114 is 450, which is larger than the opening of 400. ” (a state close to a fully open state). As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "400"). In this state, the target opening of the expansion valve 114 is controlled to gradually decrease to "400," "350," "300," and "250" as the required boiling-up capacity increases by one rank, The split ratio to the water-refrigerant heat exchanger 15 side increases.

<Summer heating operation>
Next, boiling-up operation suitable for execution in summer (hereinafter referred to as summer boiling-up operation as appropriate) will be described with reference to FIG. 11 .

During the summer boiling operation shown in FIG. 11, the four-way valve control unit 410A causes the four-way valve 31 to connect the piping portion 18c to the piping portion 18d and connect the piping portion 18a to the piping portion 18b. It is switched to the communication position (cooling position described above). The two-way valve control units 410E and 420C control the two-way valve 121 to be fully closed, the two-way valve 123 to be fully open, the two-way valve 122 to be fully closed, the two-way valve 125 to be fully closed, and the two-way valve to be fully closed. 126 is switched to a fully open state, and the two-way valve 124 is switched to a fully closed state. Further, the expansion valve control unit 410C controls the expansion valve 112 to be fully closed, the expansion valve 114 to be fully closed, the expansion valve 113 to be open (specifically, the ΔH control described above is performed), and the expansion valve 113 to be fully closed. Valve 111 is controlled to be fully open.

As a result, the piping portion 18c on the discharge side of the compressor 14 → the piping portion 18d → the piping portion 25j (two-way valve 123) → the piping portion 25b → the flow path 15b on the refrigerant side of the water-refrigerant heat exchanger 15 → the piping portion 25c ( expansion valve 111)→piping portion 25e→piping portion 18e (expansion valve 113)→outdoor heat exchanger 17→piping portion 18d→piping portion 18f→piping portion 18b→piping portion 18a on the intake side of compressor 14. It is formed. As a result, after the gaseous refrigerant sucked at low temperature and low pressure is compressed by the compressor 14 to become a high temperature and high pressure gas, the refrigerant side flow of the water-refrigerant heat exchanger 15 functioning as a condenser In the passage 15b, the water exchanges heat with the water flowing through the passage 15a on the water side, releases heat to the water, heats the water, and changes into a high-pressure liquid. The liquid refrigerant passes through the fully open expansion valve 111 and is decompressed by the expansion valve 113 to become a low-temperature, low-pressure liquid, which is easily evaporated. It absorbs heat by exchanging heat with the outside air, evaporating and changing to gas, and returns 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 supply pipe 5 connected to the lower part of the hot water storage tank 2 receives heat from the condensed refrigerant in the water-side flow path 15a of the water-refrigerant heat exchanger 15. After being heated to a high temperature, the hot water is returned into the hot water storage tank 2 through a heating return pipe 6 connected to the top of the hot water storage tank 2, so that high temperature water (heated water) is sequentially stored in the hot water storage tank 2 in a layered manner. be.

At this time, as in the winter boiling operation of FIG. The heat exchanger 27, and the piping section 25i, the piping section 25f, the piping section 25d, the communication conduit 104, the piping section 26a, the piping section 26b, and the communication that communicate with the indoor heat exchanger 27 side. The refrigerant is sealed inside the pipes 103 and the like (see the lower left table in FIG. 11).

In the above operation, the target rotation speed Nb of the compressor 14 is controlled by the compressor control section 410B as shown in FIG. Furthermore, when the outside air temperature Tair is low, the target rotation speed Nb is controlled to be high, and when the outside air temperature Tair is high, the target rotation speed Nb is controlled to be low. 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 increases when the outside air temperature Tair is low, and the fan rotation speed N2 increases when the outside air temperature Tair is high. The rotation speed is controlled to be small. The target rotation speed Nb of the compressor 14 and the rotation speed N2 of the outdoor fan are determined so as to achieve a predetermined constant boiling capacity regardless of the level of the outside air temperature Tair. there is

6, the pump control unit 420A controls the rotation speed of the boiling pump 19 so that the pump rotation speed decreases when the boiling temperature Tb is lower than the target temperature. , and when the boiling temperature Tb is higher than the target temperature, the pump rotation speed is controlled to be increased. The indoor fan 77 is stopped from rotating under the control of the indoor fan controller 430A.

As for the degree of opening of the expansion valve 113, the temperature difference ΔH=Tout between the refrigerant discharge temperature Tout and the refrigerant outflow temperature T2 is controlled by the expansion valve control unit 410C, as in the case of the winter boiling operation in FIG. The ΔH control is performed so that −T2 becomes a predetermined target temperature difference ΔHm (alternatively, the discharge control described above may be performed).

<Cooling operation>
Next, the cooling operation will be described with reference to FIG. 12 . During the cooling operation shown in FIG. 12, the four-way valve control section 410A switches the four-way valve 31 to the cooling position as in the summer boiling operation. The two-way valve control units 410E and 420C control the two-way valve 121 to be fully closed, the two-way valve 123 to be fully closed, the two-way valve 122 to be fully open, the two-way valve 125 to be fully open, and the two-way valve 126 to be fully closed. is fully closed, and the two-way valve 124 is switched to the fully closed state. Further, the expansion valve control unit 410C controls the expansion valve 112 in an open state (a known overheat control control is performed. Detailed description is omitted), the expansion valve 114 in a fully closed state, the expansion valve 113 in a fully open state, The expansion valve 111 is controlled to be fully closed.

As a result, the piping portion 18c on the discharge side of the compressor 14→piping portion 18d (two-way valve 125)→outdoor heat exchanger 17→piping portion 18e (expansion valve 113)→piping portion 25e→piping portion 25g (expansion valve 112 )→communication pipe line 103→pipe portion 26b→indoor heat exchanger 27→pipe portion 26a→communication pipe line 104→pipe portion 25d→pipe portion 25f→pipe portion 25i (two-way valve 122)→pipe portion 25m→pipe portion 18b → A refrigerant path of the piping portion 18a on the suction side of the compressor 14 is formed. As a result, the gaseous refrigerant sucked at low temperature and low pressure is compressed by the compressor 14 to become high temperature and high pressure gas, and then the outdoor heat exchanger functions as a condenser as the outdoor fan 67 rotates. At 17, it changes into a high-pressure liquid while exchanging heat with the outside air and releasing heat. The liquid refrigerant passes through the fully opened expansion valve 113 and is decompressed by the expansion valve 112 to become a low-temperature, low-pressure liquid that is easily evaporated. The indoor heat exchanger 27 absorbs heat from the indoor air, evaporates, and changes to gas, thereby cooling the air-conditioned space, and returns to the compressor 14 again as a low-temperature, low-pressure gas.

At this time, the expansion valve 111, the two-way valve 121, and the two-way valve 123 are controlled to be fully closed, thereby communicating with the water-refrigerant heat exchanger 15 and the water-refrigerant heat exchanger 15 side. The refrigerant is confined inside the piping portion 25l, the piping portion 25b, and the portion of the piping portion 25c on the side of the water-refrigerant heat exchanger 15 (the lower left table in FIG. 12). reference).

In the above operation, as in the heating operation, the rotation speed of the compressor 14 is controlled by the compressor control unit 410B so that the rotation speed of the compressor increases when the value of Tcon-Tr is large. , and when the value of Tcon-Tr is small, the compressor rotation speed is controlled to be small. The outdoor fan control unit 410D controls the outdoor fan 67 so that the outdoor fan 67 rotates at a high speed when the air conditioner is in the high power mode, and when the air conditioner is in the normal mode or the power saving mode, the fan speed is increased. The rotation speed is controlled to be small. Furthermore, in each air conditioner operation mode, the fan rotation speed is controlled to decrease when the outside air temperature Tair is low, and to increase when the outside air temperature Tair is high. The indoor fan 77 is controlled by the indoor fan control unit 430A so that the fan rotation speed increases when the Tcon-Tr value is large, and the fan rotation speed increases when the Tcon-Tr value is small. The rotation speed is controlled to be small. The boiling pump 19 is stopped from rotating under the control of the pump control section 420A.

Next, the boiling/cooling operation will be described with reference to FIG. During the boiling/cooling operation shown in FIG. 13, one of the features of this embodiment is that the four-way valve control unit 410A controls the four-way valve 31 to the cooling position (that is, the cooling (same side as driving). The two-way valve control units 410E and 420C control the two-way valve 121 to be fully closed, the two-way valve 123 to be fully open, the two-way valve 122 to be fully open, the two-way valve 125 to be fully closed, and the two-way valve 126 to be fully closed. is fully open, and the two-way valve 124 is fully closed. Further, the expansion valve control unit 410C controls the expansion valve 112 in the open state (in detail, the same ΔH control as described above is performed), the expansion valve 114 in the fully closed state, and the expansion valve 113 in the open state (details , the expansion valve 111 is controlled to be fully open.

As a result, the refrigerant path is the piping section 18c on the discharge side of the compressor 14→the piping section 18d→the piping section 25j→the piping section 25l (two-way valve 123)→the piping section 25b→the refrigerant side of the water-refrigerant heat exchanger 15. Passing through the flow path 15b → pipe portion 25c (expansion valve 111), it is divided into two at the branch point D, one of which is pipe portion 25e → pipe portion 18e (expansion valve 113) → outdoor heat exchanger 17 → pipe portion 18d → It reaches the branch point C via the pipe portion 18f (two-way valve 126), and the other is the pipe portion 25g (expansion valve 112)→communication pipe line 103→pipe portion 26b→indoor heat exchanger 27→pipe portion 26a→communication. Pipe line 104→pipe portion 25d→pipe portion 25f→pipe portion 25i (two-way valve 122)→pipe portion 25m to reach branch point C. These two routes merge at the branch point C, and the subsequent route is the branch point C→pipe section 18b→pipe section 18a on the suction side of the compressor 14 .

As a result, after the gaseous refrigerant sucked at low temperature and low pressure is compressed by the compressor 14 to become a high temperature and high pressure gas, first, the water-refrigerant heat exchanger 15 (functioning as a condenser) 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 is decompressed by the expansion valve 111 in the fully open state. After it becomes a low-temperature, low-pressure liquid and easily evaporates, it is split as described above. The one flow is further decompressed in the expansion valve 113 and then evaporated in the outdoor heat exchanger 17 (functioning as an evaporator) to absorb heat from the outside air. After further pressure reduction, the indoor heat exchanger 27 (functioning as an evaporator) absorbs heat from the indoor air, evaporates, and changes to gas to cool the air-conditioned space. Go back to 14.

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

The rotation speed of the boiling pump 19 is controlled by the pump control unit 420A when the boiling temperature Tb is lower than the target temperature, as in the winter boiling operation, the summer boiling operation, and the boiling/heating operation. When the boiling point temperature Tb is higher than the target temperature, the pump rotation speed is controlled to increase. Further, the number of revolutions of the indoor fan 77 is controlled by the indoor fan control section 430A to increase the value of Tcon-Tr based on the difference between the indoor temperature Tr and the air conditioner set temperature Tcon, as in the case of the cooling operation. When the value of Tcon-Tr is small, control is performed so that the fan speed is decreased.

The degree of opening of the expansion valve 112 is variably controlled by the expansion valve control section 410C according to the operating state of the boiling/cooling operation. Specifically, the degree of opening of the expansion valve 112 is changed 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. Feedback control is performed (so-called ΔH control similar to the above). That is, the expansion valve control unit 410C controls the opening of the expansion valve 112 in the closing direction when ΔH<ΔHm, and the opening of the expansion valve 112 in the opening direction when ΔH>ΔHm. When ΔH=ΔHm, the opening of the expansion valve 112 is maintained as it is.
Alternatively, instead of this ΔH control, feedback control of the degree of opening of the expansion valve 112 may be performed 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 of the expansion valve 112 to close when the refrigerant discharge temperature Tout is too low, and opens the expansion valve 112 when the refrigerant discharge temperature Tout is too high. Control direction.

Furthermore, the degree of opening of the expansion valve 113 is variably controlled by the expansion valve control section 410C according to the operating state of the boiling/cooling operation. Specifically, based on the indoor heat exchanger temperature Tev detected by the heat exchanger temperature sensor 36, the opening degree of the expansion valve 113 is controlled to adjust its capacity. The significance and contents of this ability adjustment control are as follows. That is, when a certain amount of time elapses from a state in which the cooling load of the object to be air-conditioned is large, such as immediately after the start of the boiling/cooling operation, and the cooling load becomes small, the cooling capacity is lower than the rated capacity in actual use. be enough. Here, if left as it is, the cooling capacity will be suppressed and the boiling capacity will also decrease, but from the viewpoint of preventing the occurrence of running out of hot water in the hot water storage tank 2, the boiling capacity will be maintained at a constant level. is preferred. Therefore, the heat exchange temperature sensor 36 is provided in the indoor heat exchanger 27, and when it is detected that the cooling capacity is lowered and the refrigerant is not sufficiently evaporated, the expansion valve 113 is controlled in response to this. , to keep the boiling capacity constant. Specifically, the valve opening degree of the expansion valve 113 is controlled to be increased in response to the decrease in the evaporating temperature detected by the heat exchanger temperature sensor 36 . As a result, the outdoor heat exchanger 17 compensates for the insufficient evaporation capacity of the indoor heat exchanger 27, and the boiling capacity of the hot water in the hot water storage tank 2 is kept constant.

In this embodiment, as another aspect of the boiling/cooling operation, the four-way valve 31 is switched to the heating position (that is, the side opposite to that during the cooling operation) as in the conventional method. It is also possible to drive in Such boiling/cooling operation will be described with reference to FIG.

The example shown in FIG. 14 is, for example, spring, autumn, etc., when the heating operation or the boiling/heating operation is performed until immediately before and the heating/cooling operation is desired in a state in which the four-way valve 31 has been switched to the heating position. (typically at the change of season, etc.), this is a suitable example of operation. That is, during the boiling/cooling operation shown in FIG. 14, the four-way valve control section 410A switches the four-way valve 31 to the heating position as described above. The two-way valve control units 410E and 420C control the two-way valve 121 to be fully open, the two-way valve 123 to be fully closed, the two-way valve 122 to be fully closed, the two-way valve 125 to be fully open, and the two-way valve 126 to be fully opened. is fully closed, and the two-way valve 124 is switched to a fully open state. Further, the expansion valve control unit 410C controls the expansion valve 112 in the open state (in detail, the same ΔH control as described above is performed), the expansion valve 114 in the fully closed state, and the expansion valve 113 in the open state (details ), and the expansion valve 111 is controlled to be fully open.

As a result, the refrigerant path is the piping portion 18c on the discharge side of the compressor 14→the piping portion 18b→the piping portion 25m→the piping portion 25a→the piping portion 25b (two-way valve 121)→the refrigerant side of the water-refrigerant heat exchanger 15. Passing through the flow path 15b → pipe portion 25c (expansion valve 111), it is divided into two at the branch point D, one is pipe portion 25e → pipe portion 18e (expansion valve 113) → outdoor heat exchanger 17 → pipe portion 18d ( The two-way valve 125) reaches the branch point A, and the other is the piping portion 25g (expansion valve 112)→communication pipeline 103→pipe portion 26b→indoor heat exchanger 27→pipe portion 26a→communication pipeline 104→ The branch point A is reached via the piping portion 25d→the piping portion 25f→the piping portion 25k (the two-way valve 124)→the piping portion 25j. These two routes merge at a branch point A, and the subsequent route is the branch point A→pipe section 18d→pipe section 18a on the suction side of the compressor 14 .

As a result, after the gaseous refrigerant sucked at low temperature and low pressure is compressed by the compressor 14 to become a high temperature and high pressure gas, first, the water-refrigerant heat exchanger 15 (functioning as a condenser) 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 is decompressed by the expansion valve 111 in the fully open state. After it becomes a low-temperature, low-pressure liquid and easily evaporates, it is split as described above. The one flow is further decompressed in the expansion valve 113 and then evaporated in the outdoor heat exchanger 17 (functioning as an evaporator) to absorb heat from the outside air. After further pressure reduction, the indoor heat exchanger 27 (functioning as an evaporator) absorbs heat from the indoor air, evaporates, and changes to gas to cool the air-conditioned space. Go back to 14.

In the above operation, the rotation speed of the compressor 14 is controlled by the compressor control section 410B based on the difference between the room temperature Tr and the air conditioner set temperature Tcon, as in the boiling/cooling operation of FIG. It is determined. The number of rotations of the outdoor fan 67 is controlled by the outdoor fan control section 410D in accordance with the outside air temperature Tair in each air conditioner operation mode in the same manner as described above, but is controlled to a lower number of rotations than during the cooling operation. be. The rotation speed of the boiling pump 19 is controlled by the pump control section 420A so that the boiling temperature Tb becomes the target temperature in the same manner as described above. Further, the number of revolutions of the indoor fan 77 is controlled by the indoor fan control section 430A based on the difference between the indoor temperature Tr and the air conditioner set temperature Tcon in the same manner as described above.

13, the opening degree of the expansion valve 112 is controlled by the expansion valve control unit 410C to determine the temperature difference ΔH= between the refrigerant discharge temperature Tout and the refrigerant outflow temperature T2. The ΔH control is performed (or the discharge control may be performed) so that Tout-T2 becomes a predetermined target temperature difference ΔHm.

Furthermore, the degree of opening of the expansion valve 113 is controlled by the expansion valve control unit 410C to distribute and supply the refrigerant to the outdoor heat exchanger 17 side and the indoor heat exchanger 27 side at a desired ratio (split flow ratio). is variably controlled by the shunting control of The details of the control contents of this flow division control will be described with reference to FIG. 15 .

FIG. 15 shows an example of a control map of the opening degree control of the expansion valve 113 executed by the expansion valve control section 410C. In the map shown in FIG. 15, the vertical axis indicates the required boiling capacity in the downward increasing direction, and the horizontal axis indicates the required cooling capacity in the downward increasing direction. It represents a relative value where "0" is "500" when the fully open state is reached.

As shown in FIG. 15, for example, when the required cooling capacity during the boiling/cooling operation is at the minimum level and the required boiling capacity is also at the minimum level, the target opening of the expansion valve 113 is the opening It is controlled to be "250" (for example, the degree of opening that is exactly intermediate between fully open and fully closed). If the required boiling capacity is increased by one rank while the required cooling capacity remains at the minimum level, the target opening of the expansion valve 113 is controlled to a slightly larger opening of "300". When the required boiling capacity is increased by one rank, the target opening of the expansion valve 113 is controlled to a slightly larger opening of "350". Control is performed so as to have a large opening of "400", and when the required boiling-up capacity is increased by one rank, the target opening of the expansion valve 113 becomes a slightly larger opening of "450" (a state close to a fully open state). controlled as As the degree of opening of the expansion valve 113 gradually increases in this way, the split flow ratio to the outdoor heat exchanger 17 side in the split flow to the outdoor heat exchanger 17 side and the indoor heat exchanger 27 side increases. controlled.

Similarly, when the required cooling capacity is one rank higher than the minimum level and the required boiling capacity is at the minimum level, the target opening of the expansion valve 113 is smaller than the opening "250". It is controlled to be "200". As a result, the split flow ratio to the indoor heat exchanger 27 side in the split flow is slightly increased (compared to the case where the opening degree is "250"). If the required boiling-up capacity is increased by one rank in this state, the target opening of the expansion valve 113 is controlled to a slightly larger opening of "250", and thereafter the required boiling-up capacity is increased by one rank. As the temperature increases, the target opening of the expansion valve 113 is controlled to gradually increase to "300", "350", and "400", and the split flow ratio to the outdoor heat exchanger 17 side increases.

Furthermore, in the same manner as described above, when the required boiling capacity is at the minimum level while the required cooling capacity is two ranks higher than the minimum level, the target opening of the expansion valve 113 is further than the opening "200". It is controlled to have a small opening of "150". As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "200"). In this state, the target opening of the expansion valve 113 is controlled to gradually increase to "200," "250," "300," and "350" as the required boiling-up capacity increases by one rank. , the split ratio to the outdoor heat exchanger 17 increases.

Furthermore, in the same manner as described above, when the required boiling capacity is at the minimum level while the required cooling capacity is three ranks higher than the minimum level, the target opening of the expansion valve 113 is further than the opening "150". It is controlled to have a small opening of "100". As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "150"). In this state, the target opening of the expansion valve 113 is controlled to gradually increase to "150," "200," "250," and "300" as the required boiling capacity increases by one rank. , the split ratio to the outdoor heat exchanger 17 increases.

Furthermore, in the same manner as described above, when the required cooling capacity is at the maximum level and the required boiling capacity is at the minimum level, the target opening of the expansion valve 113 is 50, which is smaller than the opening of 100. ” is controlled. As a result, the branch flow ratio to the indoor heat exchanger 27 side is further increased (compared to the case where the degree of opening is "100"). In this state, the target opening of the expansion valve 113 is controlled to gradually increase to "100", "150", "200", and "250" as the required boiling-up capacity increases by one rank, The diversion ratio to the outdoor heat exchanger 17 side increases.

As described above, in the heat pump water heater 1 of the present embodiment, first, by switching the four-way valve 31 to the cooling position, the cooling operation described above with reference to FIG. 12 can be performed. That is, by switching to the cooling position, the piping portion 18c on the discharge side of the compressor 14 communicates with the inlet side of the outdoor heat exchanger 17 as a condenser through the piping portion 18d. 17 is connected to the inlet side of the indoor heat exchanger 27 as an evaporator via the pipe portion 18e, the pipe portion 25e, the pipe portion 25g, the communication pipe line 103, and the pipe portion 26b. The outlet side of the indoor heat exchanger 27 is the piping on the suction side of the compressor 14 via the piping section 26a, the communication piping line 104, the piping section 25d, the piping section 25f, the piping section 25i, and the piping section 25m. It communicates with the portion 18a. As a result, the high-temperature, high-pressure refrigerant gas discharged from the compressor 14 radiates heat to the outside air in the outdoor heat exchanger 17, condenses into liquid refrigerant, and then evaporates in the indoor heat exchanger 27 to absorb heat from the indoor air. and return to the compressor 14, the cooling operation is realized.

Further, in the heat pump water heater 1 of the present embodiment, the pipe portion 18d forming the first pipe line, the pipe portions 18e, the pipe portions 25e, and the pipe portions 25g forming the second pipe line , the communication conduit 103, the piping section 26b, the piping section 18b constituting the third conduit, the piping section 25m, the piping section 25i, the piping section 25f, the piping section 25d, the communication conduit 104, apart from the pipe portion 26a, the pipe portion 25j and the pipe portion 25l constituting a fourth pipe branched from the first pipe and connected to each other by branching from the second pipe. A pipe portion 25c forming a fifth pipe line, and a pipe portion 18f forming a sixth pipe line branched from and connected to the first pipe line are provided. By using these, with the four-way valve 31 in the cooling position, it is possible to perform a boiling/cooling operation in which the hot water in the hot water storage tank is heated while cooling the indoor space.

That is, the discharge side of the compressor 14 communicates with the inlet side of the water-refrigerant heat exchanger 15 as a condenser via the piping portion 25j and the piping portion 25l branching from the branch point A of the piping portion 18d, and further The outlet side of the water-refrigerant heat exchanger 15 is connected to the branch point D through a pipe portion 25c. At this time, the branch point D is connected to the inlet side of the indoor heat exchanger 27 as an evaporator via the pipe portion 25g, the communication pipe line 103, and the pipe portion 26b. The outlet side is communicated with the suction side of the compressor 14 via the piping portion 26a, the communication pipe line 104, the piping portion 25d, the piping portion 25f, the piping portion 25i, the piping portion 25m, and the piping portion 18b. .

On the other hand, the branch point D is also connected to the outlet side of the outdoor heat exchanger 17 when functioning as a condenser (in other words, the inlet side of the outdoor heat exchanger 17 as an evaporator). The branch point provided in the first pipeline connected to the outlet side of the outdoor heat exchanger 17 as the evaporator (in other words, the inlet side of the outdoor heat exchanger 17 when functioning as a condenser) The pipe portion 18f is branched from B and connected, and this pipe portion 18f is connected to the branch point C and communicated with the suction side of the compressor .

With such a connection mode, the high-temperature and high-pressure refrigerant gas discharged from the compressor 14 is introduced into the water-refrigerant heat exchanger 15 via the piping portion 25j and the piping portion 25l, and the water-refrigerant heat exchanger 15 , heat is radiated to the hot water pipe leading to the hot water storage tank 2 and condenses to become a liquid refrigerant, which is then introduced to the branch point D via the pipe portion 25c. A part of the introduced liquid refrigerant is introduced into the indoor heat exchanger 27 from the branch point D, evaporates in the indoor heat exchanger 27, absorbs heat from the indoor air, and then flows through the pipe portion 26a and the communication pipe. While returning to the compressor 14 via the path 104, the pipe portion 25d, the pipe portion 25f, the pipe portion 25i, the pipe portion 25m, and the pipe portion 18b, the rest of the introduced liquid refrigerant is diverted. D is introduced into the outdoor heat exchanger 17 and evaporates in the outdoor heat exchanger 17 to absorb heat from the outside air. and return. In this manner, the boiling/cooling operation is realized in which the indoor space is cooled and the hot water in the hot water storage tank 2 is heated in parallel.

As described above, according to the heat pump water heater 1 of the present embodiment, both the cooling operation and the boiling/cooling operation can be performed while the four-way valve 31 is switched to the same switching position (the cooling position). can be done. As a result, unlike the conventional method in which it was necessary to switch the four-way valve 31 to a position opposite to that during cooling operation during boiling/cooling operation, interruption of operation at the time of switching the four-way valve raises the room temperature and causes a cooling sensation. can be prevented from occurring.

Further, in this embodiment, in particular, during the heating operation (see FIG. 8) in which the four-way valve 31 is in the heating position, the pipe portion 18b, the pipe portion 25m, and the pipes constituting the third pipe line The portion 25i, the pipe portion 25f, the pipe portion 25d, the communication pipe line 104, and the pipe portion 26a connect the inlet side of the indoor heat exchanger 27 on the discharge side of the compressor 14, and the pipe portion 18d connects the suction side of the compressor 14 and the outlet side of the outdoor heat exchanger 17 as an evaporator, and constitutes the second pipeline. The portion 25g, the communication pipe line 103, and the pipe portion 26b connect the inlet side of the outdoor heat exchanger 17 as an evaporator and the outlet side of the indoor heat exchanger 27 as a condenser. As a result, the high-temperature, high-pressure refrigerant gas discharged from the compressor 14 radiates heat to the indoor air in the indoor heat exchanger 27, condenses into a liquid refrigerant, and then evaporates in the outdoor heat exchanger 17 to absorb heat from the outside air. and return to the compressor 14, the heating operation can be realized.

On the other hand, the pipe portion 18b, the pipe portion 25m, the pipe portion 25i, the pipe portion 25f, the pipe portion 25d, the communication pipe line 104, and the pipe portion 26a, which constitute the third pipe line, are also connected to the branch line. It is also connected to the inlet side of the water-refrigerant heat exchanger 15 functioning as a condenser via the pipe portion 25a and the pipe portion 25b branched from the point E. As described above, the outlet side of the water-refrigerant heat exchanger 15 is connected to the branch point D through the pipe portion 25c, and the above-mentioned heat exchanger as an evaporator is connected through the pipe portion 25e and the pipe portion 18e. It will be connected to the inlet side of the outdoor heat exchanger 17 .

With such a connection mode, among the high-temperature and high-pressure refrigerant gas discharged from the compressor 14, the remainder other than the one that flows in the route of the indoor heat exchanger 27 → the outdoor heat exchanger 17 and performs the heating is , to the piping portion 25a and the piping portion 25b and introduced into the water-refrigerant heat exchanger 15 via them, where heat is released to the hot water pipe leading to the hot water storage tank 2 in the water-refrigerant heat exchanger 15 and condensed. , the condensed liquid refrigerant can be merged at the branch point D and introduced into the outdoor heat exchanger 17 . As a result, it is possible to realize a boiling-up/heating operation in which heating of the indoor space and heating of the hot water in the hot water storage tank 2 are simultaneously performed.

As a result, according to the heat pump water heater 1 of the present embodiment, both the heating operation and the boiling/heating operation can be performed while the four-way valve 31 is switched to the same switching position (the heating position). .
As a result, the cooling operation and the boiling/cooling operation can be performed at the same switching position (the cooling position) of the four-way valve 31, and the heating operation and the boiling/heating operation can be performed at the same switching position of the four-way valve 31. It can be done in the switching position (the heating position). In other words, the switching position of the four-way valve 31 is set at least during cooling operation (cooling operation, boiling/cooling operation) and at least during heating operation (heating operation, boiling/heating operation). , can be unified.

Further, particularly in the present embodiment, the two-way valve 123 is provided in the pipe portion 25l of the pipe portion 25j and the pipe portion 25l that constitute the fourth pipe line, and the pipe portion that constitutes the sixth pipe line. The two-way valve 126 is provided at 18f. As a result, for example, with the four-way valve 31 in the cooling position, the cooling operation (see FIG. 12) is executed by closing the two-way valves 123 and 126, and the two-way valves 123 and 126 are closed. The boiling/cooling operation (see FIG. 13) can be executed by opening the valve. Further, for example, by closing the two-way valves 123 and 126 and setting the four-way valve 31 to the heating position, the heating operation (see FIG. 8) or the boiling/heating operation (FIG. 9) can be performed. .

Moreover, particularly in this embodiment, a two-way valve 125 for opening and closing the section is provided between the branch point A and the branch point B in the pipe portion 18d. As a result, the two-way valve 125 is closed and the section between the branch point A and the branch point C is closed, so that during the boiling/cooling operation shown in FIG. Refrigerant flow of part 18d → branch point A → pipe part 25j → pipe part 25l → . can be reliably separated from the refrigerant flow.

In addition, particularly in this embodiment, the two-way valve 122 allows the piping portion 25i, the piping portion 25f, the piping portion 25d, the communication pipe line 104, the piping portion 25d, the piping portion 25f, the piping portion 25d, and the indoor heat exchanger 27 side of the branch point E to The pipe portion 26a is configured to be closable, and the expansion valve 112 enables the pipe portion 25g on the indoor heat exchanger 27 side of the branch point D, the communication pipe line 103, and the pipe portion 26b to be closable. It is configured. That is, by closing the two-way valve 122 and the expansion valve 112, the two-way valve 122-the piping portion 25f-the piping portion 25d-the communicating pipe line 104-the piping portion 26a-the indoor heat exchanger 27-the pipe portion 26b-the communication pipe 103-the expansion valve 112 is defined as a closed section, and the refrigerant in this section can be confined to eliminate refrigerant flow.

As a result, if the four-way valve 31 is placed in the cooling position, as shown in FIG. 11, the compressor 14 discharge side→the piping portion 25j→the piping portion 25l→the water-refrigerant heat exchanger 15→the piping portion 25c→ The hot water in the hot water storage tank 2 is heated in the route of the piping portion 25e→the piping portion 18e→the outdoor heat exchanger 17→the piping portion 18f→the suction side of the compressor 14, thereby realizing the summer boiling-up operation. be able to. That is, in this case, the boiling operation can be realized at the switching position (the cooling position) of the four-way valve 31 common to the cooling operation (see FIG. 12) and the boiling/cooling operation (see FIG. 13). As a result, the cooling operation, the boiling/cooling operation, and the summer boiling operation can be switched without switching the four-way valve 31 .

Alternatively, if the four-way valve 31 is set to the heating position, as shown in FIG. The hot water in the hot water storage tank 2 is heated through the route of the heat exchanger 15 → the pipe portion 25c → the pipe portion 25e → the pipe portion 18e → the outdoor heat exchanger 17 → the pipe portion 18d → the suction side of the compressor 14. It is possible to realize a winter boiling operation that heats. That is, in this case, the heating operation (see FIG. 8) and the boiling/heating operation (see FIG. 9) can be performed at the switching position (heating position) of the four-way valve 31 common to the heating operation. As a result, the heating operation, the boiling/heating operation, and the winter boiling operation can be performed without switching the four-way valve 31 .

It should be noted that the present invention is not limited to the embodiments described above, and can be applied without changing the gist of the present invention. Such modifications will be described below.

(1) Case of automatic switching between winter boiling-up operation and summer boiling-up operation As described above, in the heat pump water heater 1, the winter boiling-up operation described with reference to FIG. and the summer boiling operation described with reference to FIG. 11 can be selectively executed. Correspondingly, when the boiling-up operation is instructed via the remote controller 60 or the like, the winter boiling-up operation and the summer boiling-up operation are automatically switched according to a predetermined operation switching factor (described later). Either one may be selected. Such a modified example will be described with reference to FIG.

FIG. 16 shows that the heat pump control unit 410, the hot water storage control unit 420, and the air conditioner control unit 430 cooperate with each other in this modification (or at least one of them may cooperate with others). ) is a flow chart showing a control procedure. In this example, a case will be described in which the outside air temperature Tair detected by the outside air temperature sensor 22 is used as the operation switching factor.

In FIG. 16, first, in step S10, the heat pump control unit 410, the hot water storage control unit 420, and the air conditioner control unit 430 (hereinafter simply referred to as "control unit 410, etc.") It is determined whether or not an instruction to drive has been given. If there is no boiling-up operation instruction, the determination is not satisfied (S10: NO), and this flow ends. If there is an instruction for boiling operation, the determination is satisfied (S10: YES), and the process moves to step S20.

In step S20, the control unit 410 or the like controls that the outside air temperature Tair detected by the outside air temperature sensor 22 is a predetermined temperature (for example, an appropriate temperature in the range of 10°C to 20°C, such as 15°C). etc.) is determined as follows. If the temperature exceeds the predetermined temperature, the determination is not satisfied (S20: NO), and the process proceeds to step S50, which will be described later.

In step S30, the controller 410 and the like switch the four-way valve 31 to the heating position by the four-way valve controller 410A. After that, the process moves to step S40.

In step S40, the control unit 410 and the like switch the two-way valves 121 and 125 to the fully open state and the two-way valves 123, 122, 126 and 124 to the fully closed state by the two-way valve control units 410E and 420C. The expansion valve control unit 410C sets the expansion valves 112 and 114 to the fully closed state and the expansion valve 111 to the fully open state, and performs the ΔH control on the expansion valve 113, so that the winter boiling time described above with reference to FIG. Run up. After that, this flow ends.

On the other hand, in step S50 where the determination in step S20 is not satisfied, the controller 410 and the like switch the four-way valve 31 to the cooling position by the four-way valve controller 410A. After that, the process moves to step S60.

In step S60, the control unit 410 and the like switch the two-way valves 123 and 126 to the fully open state and the two-way valves 121, 122, 125 and 124 to the fully closed state by the two-way valve control units 410E and 420C. The expansion valve control unit 410C sets the expansion valves 112 and 114 to the fully closed state and the expansion valve 111 to the fully open state, and performs the ΔH control on the expansion valve 113, so that the summer boiling described above with reference to FIG. Run up. After that, this flow ends.

Among the valve control functions of the two-way valve control units 410E and 420C and the expansion valve control unit 410C, the function of controlling the opening and closing of the two-way valve 123 and the expansion valve 112 corresponds to opening/closing control means. ing.

In the present modification, as described above, when the heating operation is instructed via the remote controller 60, whether the cooling position corresponding to the cooling operation or the like should be set or the heating position corresponding to the heating operation or the like. Switching control of the four-way valve 31 is performed according to a predetermined operation switching factor (the outside air temperature Tair in the above example), which serves as an index of whether to switch.

That is, when the boiling-up operation is performed, for example, when the outside air temperature Tair is relatively low, the four-way valve 31 is considered to be switched to correspond to the heating operation, etc., and is switched to the heating position. be done. As a result, the winter boiling operation is executed with the four-way valve 31 switched to the heating position. However, the four-way valve 31 remains in the same heating position, and the operation can be smoothly shifted. As a result, it is possible to reliably prevent a decrease in room temperature (decrease in feeling of heating) due to suspension of operation such as when the switching position of the four-way valve 31 is changed.

Conversely, when the boiling-up operation is performed, for example, when the outside air temperature Tair is relatively high, the four-way valve 31 is considered to be switched to correspond to the cooling operation, etc., and is switched to the cooling position. can be switched. As a result, the summer boiling operation is executed with the four-way valve 31 switched to the cooling position. However, the four-way valve 31 remains in the same cooling position, and the operation can be smoothly shifted.

As a result, according to this modified example, it is possible to reliably prevent an increase in room temperature (decrease in cooling sensation) due to suspension of operation such as when the switching position of the four-way valve 31 is changed.

In the above description, the outside air temperature Tair detected by the outside air temperature sensor 22 is used as an example of the operation switching factor, but it is not limited to this. That is, the average value of the outside air temperature Tair within a predetermined period (for example, a plurality of days in the past), the temperature of the water supplied to the hot water storage tank 2 to the water supply pipe 7, or the average value within the predetermined period, or the predetermined period ( For example, the performance of the operation mode of the cooling operation or the heating operation (or the instruction performance of the operation mode) within a plurality of days in the past may be used. When the water supply temperature is used, for example, in step S20, if the water supply temperature is equal to or lower than a predetermined value, the process proceeds to step S30, and if the water supply temperature exceeds the predetermined value, the process proceeds to step S50. When using the actual operation performance (or the actual operation instruction performance), for example, in step S20, if the performance of mainly heating operation or boiling/heating operation is large, the process proceeds to step S30, and mainly the cooling operation or heating operation is performed. If the performance of the top/cooling operation is large, the process proceeds to step S50. In these cases, the same effect as described above is obtained.
Further, in the above example, when the instruction for the boiling operation is given via the remote control 60 or the like, the selection of the winter boiling operation or the summer boiling operation is executed. is not limited to this. That is, for example, in a boiling operation that is regularly and periodically performed at a predetermined timing or a desired timing (such as a nighttime boiling operation that is usually performed at midnight every day), at that timing, according to the operation switching factor Either one of the winter boiling-up operation and the summer boiling-up operation may be selected. Further, regardless of the execution of the boiling-up operation, the four-way valve 31 is set to the heating position or the It may be switched to the cooling position (although the boiling operation is not performed yet, the switch may be completed in advance before the boiling operation is performed).

(2) Others For example, at least one of the two-way valves 121 to 125 may be replaced with an expansion valve with a closing function. Also, instead of the expansion valves 111 to 114, an ejector may be used as a decompressor.

Also, the flowchart shown in FIG. 16 does not limit the present invention to the procedures shown in the above flow, and additions, deletions, or changes in the order of procedures may be made within the scope of the gist and technical idea of the invention. good.

In addition to the methods already described above, the methods according to the above-described embodiments and modifications may be appropriately combined and used.

In addition, although not exemplified one by one, the present invention can be implemented with various modifications within the scope of the invention.

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)
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 pipe 18b pipe portion (third pipe line)
18d piping section (first pipeline)
18e Piping part (second pipe line)
18f Piping section (6th pipeline)
25a piping section (seventh pipeline)
25b piping section (seventh pipeline)
25c piping part (5th pipeline)
25d piping section (third pipeline)
25e piping section (second pipeline)
25f piping section (third pipeline)
25g piping section (second pipeline)
25i piping section (third pipeline)
25j Piping section (4th pipeline)
25l piping section (4th pipeline)
25m piping section (third pipeline)
26a piping section (third pipeline)
26b piping section (second pipeline)
27 indoor heat exchanger 30 refrigerant circulation circuit 31 four-way valve 67 outdoor fan 77 indoor fan 100 hot water storage unit 103 communication pipe (second pipe)
104 Communication conduit (third conduit)
111 expansion valve 112 expansion valve (fifth on-off valve)
113 Expansion valve 114 Expansion valve 121 Two-way valve 122 Two-way valve (fourth on-off valve)
123 two-way valve (first on-off valve)
124 two-way valve 125 two-way valve (third on-off valve)
126 two-way valve (second on-off valve)
200 heat pump unit (outdoor unit)
300 air conditioner unit (indoor unit)
410 heat pump control unit 410A four-way valve control unit (four-way valve control means)
410C expansion valve control unit 410E two-way valve control unit 420 hot water storage control unit 420C two-way valve control unit 430 air conditioner control unit A branch point (first branch point)
B branch point (third branch point)
C branch point (fourth branch point)
D branch point (second branch point)
Tair outside temperature

Claims (5)

a heat pump heat exchanger capable of selectively functioning as a condenser or an evaporator for heat exchange between refrigerant and ambient air;
a compressor connected to the heat pump heat exchanger;
a hot water storage tank for storing hot water;
a water-refrigerant heat exchanger as a condenser that exchanges heat between the refrigerant and water;
an indoor heat exchanger capable of selectively functioning as a condenser or an evaporator for exchanging heat between the refrigerant and indoor air;
forming a hot water circulation circuit by annularly connecting the water side of the water-refrigerant heat exchanger and the hot water storage tank with a hot water pipe;
In a heat pump water heater with a cooling and heating function in which the heat pump heat exchanger, the compressor, the refrigerant side of the water-refrigerant heat exchanger, and the indoor heat exchanger are connected by refrigerant pipes to form a refrigerant circulation circuit,
a first switching position in which the discharge side of the compressor is communicated with the heat pump heat exchanger as a condenser and the suction side of the compressor is communicated with the indoor heat exchanger as an evaporator; a four-way valve that can be switched to a second switching position that communicates the discharge side with the indoor heat exchanger as a condenser and communicates the suction side of the compressor with the heat pump heat exchanger as an evaporator;
a first pipeline, one side of which communicates with the discharge side of the compressor via the four-way valve in the first switching position and the other side of which is connected to the inlet side of the heat pump heat exchanger as a condenser;
a second pipeline connecting the outlet side of the heat pump heat exchanger as a condenser and the inlet side of the indoor heat exchanger as an evaporator;
a third pipeline, one side of which communicates with the suction side of the compressor via the four-way valve in the first switching position, and the other side of which is connected to the outlet side of the indoor heat exchanger as an evaporator;
a fourth pipeline having one side branched from a first branch point provided in the first pipeline and having the other side connected to the inlet side of the water-refrigerant heat exchanger as a condenser;
a fifth pipeline having one side branched from a second branch point provided in the second pipeline and having the other side connected to the outlet side of the water-refrigerant heat exchanger as a condenser;
One side is branched from a third branch point provided in the first pipeline and connected to the outlet side of the heat pump heat exchanger as an evaporator, and the other side is a fourth branch provided in the third pipeline. a sixth pipe branching from a point and communicating with the suction side of the compressor via the four-way valve in the first switching position;
four-way valve control means for switching the four-way valve between the first switching position and the second switching position;
a seventh pipeline having one side branched from a fifth branch point provided in the third pipeline and having the other side connected to the inlet side of the water-refrigerant heat exchanger as a condenser;
has
When the four-way valve is in the second switching position,
The third conduit is
connecting the discharge side of the compressor and the inlet side of the indoor heat exchanger as a condenser;
The first conduit is
connecting the suction side of the compressor and the outlet side of the heat pump heat exchanger as an evaporator;
The second conduit is
connecting the outlet side of the indoor heat exchanger as a condenser and the inlet side of the heat pump heat exchanger as an evaporator;
A heat pump water heater with a cooling and heating function, characterized by: a first on-off valve provided in the fourth pipeline for opening and closing the fourth pipeline;
a second on-off valve provided in the sixth pipeline for opening and closing the sixth pipeline;
The heat pump water heater with a cooling and heating function according to claim 1 , characterized by comprising: 3. The cooling/heating function according to claim 2 , further comprising a third on-off valve that is provided in a section between the first branch point and the third branch point in the first pipeline and that opens and closes the section. heat pump water heater. a fourth on-off valve capable of closing the indoor heat exchanger side of the third pipeline with respect to the fifth branch point;
a fifth on-off valve capable of closing the indoor heat exchanger side of the second branch point in the second pipeline;
3. The heat pump water heater with cooling and heating function according to claim 2 , characterized by comprising: 5. The four-way valve control means switches the four -way valve to either the first switching position or the second switching position according to a predetermined operation switching factor. The heat pump water heater with cooling and heating functions according to item 1.

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