WO2021220486A1

WO2021220486A1 - Refrigeration cycle device

Info

Publication number: WO2021220486A1
Application number: PCT/JP2020/018319
Authority: WO
Inventors: 駿哉行徳; 悟梁池
Original assignee: 三菱電機株式会社
Priority date: 2020-04-30
Filing date: 2020-04-30
Publication date: 2021-11-04
Also published as: EP4145028A1; EP4145028A4; CN115461561A; JPWO2021220486A1; US20230099489A1; JP7317224B2

Abstract

A refrigeration cycle device (1000) comprises a refrigerant circuit that includes a compressor (1), a flow-channel-switching part (2), an outdoor heat exchanger (3), decompression devices (4A, 4B), a first indoor heat exchanger (5A), a first connecting pipe (10), and a second connecting pipe (11). Refrigerant is circulated through the refrigerant circuit. The refrigerant circuit furthermore includes a first three-way valve (8A) positioned downstream of the first indoor heat exchanger in a cooling operation state and positioned upstream of the first indoor heat exchanger in a heating operation state, and a second three-way valve (9A) positioned upstream of the first indoor heat exchanger in the cooling operation state and positioned downstream of the first indoor heat exchanger in the heating operation state. Respective first opening parts (P1) of the first three-way valve and the second three-way valve are connected to one end or another end of the first indoor heat exchanger in the refrigerant circuit. Respective second opening parts (P2) of the first three-way valve and the second three-way valve are connected to the first connecting pipe. Respective third opening parts (P3) of the first three-way valve and the second three-way valve are connected to the second connecting pipe. The first three-way valve and the second three-way valve are switched independently of each other in each of a first state in which a valve body (15) is in a first position, a second state in which the valve body is in a second position, and a third state in which the valve body is in a third position. A first space (S1) that communicates with the first opening parts and the second opening parts and is sectioned off from the third opening parts is disposed in a valve chamber (16) in the first state, a second space (S2) that communicates with the first opening parts, the second opening parts, and the third opening parts is disposed in the valve chamber in the second state, and a third space (S3) that communicates with the first opening parts and the third opening parts and is sectioned off from the second opening parts is disposed in the valve chamber in the third state.

Description

Refrigeration cycle equipment

This disclosure relates to a refrigeration cycle device.

Conventionally, a refrigeration cycle device including an outdoor unit, a plurality of indoor units, and a repeater, in which the outdoor unit and the plurality of indoor units are connected via the repeater is known.

Japanese Patent Application Laid-Open No. 4-6361 discloses the refrigeration cycle device in which the outdoor unit and the repeater are connected via the first refrigerant pipe and the second refrigerant pipe. The refrigeration cycle device includes a first refrigerant flow path switching mechanism arranged in the outdoor unit and a second refrigerant flow path switching mechanism arranged in the repeater.

The first flow path switching mechanism includes one four-way valve and four check valves. The first refrigerant flow path mechanism switches between a cooling operation state in which the outdoor heat exchanger acts as a condenser and a heating operation state in which the outdoor heat exchanger acts as an evaporator, and the cooling operation state. Regardless of switching to the heating operation state, the state in which the pressure of the refrigerant flowing through the first refrigerant pipe is lower than the pressure of the refrigerant flowing through the second refrigerant pipe is maintained. The inner diameter of the first refrigerant pipe is larger than the inner diameter of the second refrigerant pipe. As a result, in the refrigeration cycle device, an increase in pressure loss in the first refrigerant pipe and the second refrigerant pipe due to switching between the cooling operation state and the heating operation state is suppressed, and a decrease in operating capacity is suppressed. There is.

Further, the second flow path switching mechanism includes a plurality of flow path switching valves. By the second refrigerant flow path mechanism, in the first operating state or the second operating state, a plurality of all cooling operation states or all heating operation states in which all of the plurality of indoor units act as evaporators or condensers, and a plurality of indoor units. It is possible to switch between a cooling-based operating state and a heating-based operating state in which a part of the indoor unit acts as a condenser and the other part of the plurality of indoor units acts as an evaporator.

Japanese Unexamined Patent Publication No. 4-6361

In the above refrigeration cycle device, when the load of the indoor heat exchanger is reduced, it is necessary to reduce the drive frequency of the compressor to reduce the circulation amount of the refrigerant in order to prevent a decrease in comfort.

However, in the refrigeration cycle device, when the circulation amount of the refrigerant decreases, the differential pressure before and after the check valve constituting the first flow path switching mechanism decreases, so that chattering occurs.

A main object of the present disclosure is to provide a refrigeration cycle apparatus in which the occurrence of chattering is suppressed while preventing a decrease in comfort when the load of the indoor heat exchanger is reduced.

The refrigeration cycle apparatus according to the present disclosure includes a compressor, a flow path switching unit, an outdoor heat exchanger, a decompression device, a first indoor heat exchanger, a first connection pipe through which a refrigerant flowing into the first indoor heat exchanger flows, and It includes a second connecting pipe through which the refrigerant flowing out of the first indoor heat exchanger flows, and includes a refrigerant circuit through which the refrigerant circulates. The flow path switching unit switches between a cooling operation state in which the outdoor heat exchanger acts as a condenser and a heating operation state in which the outdoor heat exchanger acts as an evaporator. The refrigerant circuit is arranged in the cooling operation state with the first three-way valve arranged downstream from the first room heat exchanger in the cooling operation state and upstream from the first room heat exchanger in the heating operation state. Further includes a second three-way valve located upstream of the first chamber heat exchanger and downstream of the first chamber heat exchanger in the heating operating state. Each of the first three-way valve and the second three-way valve has a valve seat including a valve chamber and a first opening, a second opening, and a third opening connected to the valve chamber, and a first valve chamber. Includes a position, a second position, and a valve body that moves between the third positions. The first openings of each of the first three-way valve and the second three-way valve are connected to one end or the other end of the first chamber heat exchanger in the refrigerant circuit. The second opening of each of the first three-way valve and the second three-way valve is connected to the first connection pipe. The third opening of each of the first three-way valve and the second three-way valve is connected to the second connecting pipe. Each of the first three-way valve and the second three-way valve has a first state in which the valve body is in the first position, a second state in which the valve body is in the second position, and a second state in which the valve body is in the third position. It can be switched to any of the three states independently of each other. In each of the first three-way valve and the second three-way valve, in the first state, a first space communicating with the first opening and the second opening and partitioned from the third opening is arranged in the valve chamber, and the first space is arranged. In the second state, a second space communicating with the first opening, the second opening, and the third opening is arranged in the valve chamber, and in the third state, communicating with the first opening and the third opening. A third space partitioned from the second opening is arranged in the valve chamber.

According to the present disclosure, it is possible to provide a refrigeration cycle device in which the occurrence of chattering is suppressed while preventing a decrease in comfort when the load of the indoor heat exchanger is reduced.

It is a figure which shows the refrigerant circuit of the refrigerating cycle apparatus which concerns on this embodiment. It is sectional drawing which shows the valve seat, the valve chamber, and the valve body when the 1st three-way valve which concerns on this Embodiment is in a 1st state. It is sectional drawing seen from the arrow III-III shown in FIG. It is sectional drawing which shows the valve seat, the valve chamber, and the valve body when the 1st three-way valve which concerns on this embodiment is in a 2nd state. It is sectional drawing seen from the arrow VV shown in FIG. It is sectional drawing which shows the valve seat, the valve chamber, and the valve body when the 1st three-way valve which concerns on this embodiment is in a 3rd state. It is sectional drawing seen from the arrow VII-VII shown in FIG. It is a figure which shows the refrigerant circuit when the refrigerating cycle apparatus which concerns on this embodiment is in a state of total cooling operation. It is a figure which shows the refrigerant circuit when the load of the 1st room heat exchanger is lower than the state shown in FIG. 8 when the refrigerating cycle apparatus which concerns on this embodiment is in the state of total cooling operation. It is a figure which shows the refrigerant circuit when the refrigerating cycle apparatus which concerns on this embodiment is in a state of full heating operation. It is a figure which shows the refrigerant circuit when the load of the 1st room heat exchanger is lower than the state shown in FIG. 10 when the refrigerating cycle apparatus which concerns on this embodiment is in a full heating operation state. It is a figure which shows the refrigerant circuit when the refrigerating cycle apparatus which concerns on this embodiment is in the 1st cooling main body operation state. It is a figure which shows the refrigerant circuit when the refrigerating cycle apparatus which concerns on this embodiment is in the 1st heating main operation state. FIG. 2 is a cross-sectional view showing a valve seat, a valve chamber, and a valve body when a modified example of the first three-way valve shown in FIG. 2 is in the first state. FIG. 2 is a cross-sectional view showing a valve seat, a valve chamber, and a valve body when a modified example of the first three-way valve shown in FIG. 2 is in the second state. FIG. 2 is a cross-sectional view showing a valve seat, a valve chamber, and a valve body when a modified example of the first three-way valve shown in FIG. 2 is in the third state.

Hereinafter, embodiments will be described with reference to the drawings. In the drawings below, the same or corresponding parts are given the same reference number and the explanation is not repeated.

<Configuration of refrigeration cycle equipment>
As shown in FIG. 1, the refrigerating cycle device 1000 according to the present embodiment includes a refrigerant circuit in which a refrigerant circulates. The refrigerant circuit includes a compressor 1, a four-way valve 2 as a flow path switching unit, an outdoor heat exchanger 3, a first decompression device 4A, a second decompression device 4B, a first indoor heat exchanger 5A, and a second indoor heat exchanger. 5B, 1st check valve 6A, 2nd check valve 6B, 3rd check valve 6C, 4th check valve 6D, gas-liquid separator 7, 1st three-way valve 8A, 2nd three-way valve 9A, 3rd It includes a three-way valve 8B, a fourth three-way valve 9B, a first connection pipe 10, a second connection pipe 11, a third connection pipe 12A, a fourth connection pipe 13A, a fifth connection pipe 12B, and a sixth connection pipe 13B.

The compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the first check valve 6A, the second check valve 6B, the third check valve 6C, and the fourth check valve 6D are housed in the outdoor unit 100. ing. The first decompression device 4A and the first indoor heat exchanger 5A are housed in the first indoor unit 200A. The second decompression device 4B and the second indoor heat exchanger 5B are housed in the second indoor unit 200B. The gas-liquid separator 7, the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B are housed in the repeater 300.

The first connection pipe 10 and the second connection pipe 11 are arranged between the outdoor unit 100 and the repeater 300 to connect the two. The third connection pipe 12A and the fourth connection pipe 13A are arranged between the first indoor unit 200A and the repeater 300 and connect them. The fifth connection pipe 12B and the sixth connection pipe 13B are arranged between the second indoor unit 200B and the repeater 300 to connect the second indoor unit 200B and the repeater 300.

The compressor 1 has a discharge port for discharging the refrigerant and a suction port for sucking the refrigerant. The compressor 1 is, for example, a constant speed compressor having a constant drive frequency. The compressor 1 may be, for example, an inverter compressor whose drive frequency is controlled by an inverter.

The four-way valve 2 has the first to fourth ports. The first port is connected to the discharge port of the compressor 1. The second port is connected to the suction port of the compressor 1. The third port is connected to the first connection pipe 10 via the outdoor heat exchanger 3 and the first check valve 6A, and is connected to the second connection via the outdoor heat exchanger 3 and the second check valve 6B. It is connected to the pipe 11. The fourth port is connected to the first connecting pipe 10 via the third check valve 6C, and is connected to the second connecting pipe 11 via the fourth check valve 6D. The four-way valve 2 has a cooling operation state in which the first port and the third port communicate with each other and the second port and the fourth port communicate with each other, and the first port and the fourth port communicate with each other and the second port and the second port communicate with each other. Switch between the heating operation state in which the 3 ports communicate with each other.

In the outdoor heat exchanger 3, the refrigerant circulating in the refrigerant circuit and the outdoor air exchange heat. The first decompression device 4A and the second decompression device 4B are, for example, expansion valves. In the first decompression device 4A and the second decompression device 4B, the refrigerant expands. In the first indoor heat exchanger 5A and the second indoor heat exchanger 5B, the refrigerant circulating in the refrigerant circuit and the indoor air exchange heat. The first indoor unit 200A and the second indoor unit 200B are arranged in different living rooms, for example.

Inside the outdoor unit 100, a refrigerant flow path connecting the outdoor heat exchanger 3 and the first connection pipe 10, a refrigerant flow path connecting the outdoor heat exchanger 3 and the second connection pipe 11, four sides. A refrigerant flow path connecting the fourth port of the valve 2 and the first connecting pipe 10 and a refrigerant flow path connecting the fourth port of the four-way valve 2 and the second connecting pipe 11 are formed. There is.

The first check valve 6A is arranged in the refrigerant flow path between the outdoor heat exchanger 3 and the first connection pipe 10, and only the refrigerant flowing from the outdoor heat exchanger 3 to the first connection pipe 10 flows. The first check valve 6A shuts off the flow of the refrigerant flowing from the first connection pipe 10 to the outdoor heat exchanger 3.

The second check valve 6B is arranged in the refrigerant flow path between the outdoor heat exchanger 3 and the second connection pipe 11, and only the refrigerant flowing from the second connection pipe 11 to the outdoor heat exchanger flows. The second check valve 6B shuts off the flow of the refrigerant flowing from the second connection pipe 11 to the outdoor heat exchanger 3.

The third check valve 6C is arranged in the refrigerant flow path between the fourth port of the four-way valve 2 and the first connecting pipe 10, and only the refrigerant flowing from the fourth port of the four-way valve 2 to the second connecting pipe. Shed. The third check valve 6C shuts off the flow of the refrigerant flowing from the first connection pipe 10 to the fourth port of the four-way valve 2.

The fourth check valve 6D is arranged in the refrigerant flow path between the fourth port of the four-way valve 2 and the second connection pipe 11, and the refrigerant flows from the second connection pipe 11 to the fourth port of the four-way valve 2. Only shed. The fourth check valve 6D shuts off the flow of the refrigerant flowing from the fourth port of the four-way valve 2 to the second connecting pipe 11.

The gas-liquid separator 7 is connected to the first connection pipe 10, and has an inflow port 71 into which the refrigerant flows in, a first outflow port 72 in which the gas-phase refrigerant flows out, and a second outflow port 73 in which the liquid-phase refrigerant flows out. And have.

The configurations of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B are equal to each other. As shown in FIGS. 2 to 7, each of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B includes a valve seat 14 and a valve body 15.

The valve seats 14 of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B are the valve chamber 16 and the first opening P1 and the first opening P1 communicating with the valve chamber 16. Includes two openings P2 and a third opening P3.

The valve seat 14 faces the valve chamber 16 and has a first surface 14A on which one ends of the first opening P1 and the third opening P3 are arranged and one end of the second opening P2. It has a second surface 14B. The first opening P1 is arranged side by side with the third opening P3 at a distance in the circumferential direction as the first direction. The opening area of the third opening P3 is, for example, equal to the opening area of the first opening P1. The second surface 14B faces the first surface 14A with the valve body 15 interposed therebetween, for example, in the Z direction as the second direction. The second opening P2 is arranged so as to overlap the rotation axis of the valve body 15 when viewed from the Z direction, for example. When viewed from the Z direction, the shortest distance between the centers of the second opening P2 and the first opening P1 is equal to, for example, the shortest distance between the centers of the second opening P2 and the third opening P3.

The first opening P1 of the first three-way valve 8A is connected to the first chamber heat exchanger 5A via the third connection pipe 12A. The second opening P2 of the first three-way valve 8A is connected to the first outlet 72 of the gas-liquid separator 7. That is, the second opening P2 of the first three-way valve 8A is connected to the first connection pipe 10 via the gas-liquid separator 7. The third opening P3 of the first three-way valve 8A is connected to the second connecting pipe 11.

The first opening P1 of the second three-way valve 9A is connected to the first chamber heat exchanger 5A via the fourth connecting pipe 13A. The second opening P2 of the second three-way valve 9A is connected to the second outlet 73 of the gas-liquid separator 7. That is, the second opening P2 of the second three-way valve 9A is connected to the first connection pipe 10 via the gas-liquid separator 7. The third opening P3 of the second three-way valve 9A is connected to the second connecting pipe 11.

The first opening P1 of the third three-way valve 8B is connected to the second chamber heat exchanger 5B via the fifth connection pipe 12B. The second opening P2 of the third three-way valve 8B is connected to the first outlet 72 of the gas-liquid separator 7. That is, the second opening P2 of the third three-way valve 8B is connected to the first connection pipe 10 via the gas-liquid separator 7. The third opening P3 of the third three-way valve 8B is connected to the second connecting pipe 11.

The first opening P1 of the fourth three-way valve 9B is connected to the second chamber heat exchanger 5B via the sixth connection pipe 13B. The second opening P2 of the fourth three-way valve 9B is connected to the second outlet 73 of the gas-liquid separator 7. That is, the second opening P2 of the fourth three-way valve 9B is connected to the first connection pipe 10 via the gas-liquid separator 7. The third opening P3 of the fourth three-way valve 9B is connected to the second connecting pipe 11.

The second opening P2 of the first three-way valve 8A and the second opening P2 of the third three-way valve 8B are connected in parallel to the first outlet 72 and the first connection pipe 10 of the gas-liquid separator 7. ing. The third opening P3 of the first three-way valve 8A and the third opening P3 of the third three-way valve 8B are connected in parallel to the second connection pipe 11.

The second opening P2 of the second three-way valve 9A and the second opening P2 of the fourth three-way valve 9B are connected in parallel to the second outlet 73 of the gas-liquid separator 7 and the first connection pipe 10. ing. The third opening P3 of the second three-way valve 9A and the third opening P3 of the fourth three-way valve 9B are connected to each other in parallel with the second connection pipe 11.

The valve bodies 15 of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B are in the first position, the second position, and the third position in the valve chamber 16. Move between positions. The valve body 15 is provided so as to rotate about, for example, a rotation axis extending along the Z direction. The valve body 15 rotates, for example, in the circumferential direction from the third opening P3 toward the first opening P1 and vice versa. The valve body 15 is connected to a rotating shaft of a motor (not shown) via, for example, a gear 17. The valve body 15 is arranged side by side with the third surface 18 sliding with the first surface 14A and the third surface 18 in the circumferential direction as the first direction, and is recessed with respect to the third surface 18. It has a recess 19 and a fourth surface 20 which is located on the opposite side of the third surface 18 and which faces the second surface 14B of the valve seat 14 at a distance in the Z direction.

The valve body 15 has a first end portion 151 in the circumferential direction and a second end portion 152 located on the opposite side of the first end portion 151 in the circumferential direction. The first end portion 151 is an end portion arranged in front of the second end portion 152 when the valve body 15 rotates in the circumferential direction from the third opening P3 toward the first opening P1. The second end portion 152 is an end portion arranged in front of the first end portion 151 when the valve body 15 rotates in the circumferential direction from the first opening P1 to the third opening P3.

The recess 19 has a third end portion 191 in the circumferential direction and a fourth end portion 192 located on the opposite side of the third end portion 191 in the circumferential direction. The third end 191 is behind the first end 151 and more than the fourth end 192 when the valve body 15 rotates in the circumferential direction from the third opening P3 to the first opening P1. It is the end that is placed in the front. The fourth end 192 is behind the second end 152 and more than the third end 191 when the valve body 15 rotates in the circumferential direction from the first opening P1 to the third opening P3. It is the end that is placed in the front.

The circumferential distance between the first end 151 and the third end 191 is wider than the circumferential distance between the second end 152 and the fourth end 192. The third surface 18 is arranged at least in the circumferential direction between the first end portion 151 and the third end portion 191 and around the entire circumference of the recess 19.

As shown in FIG. 4, when the valve body 15 is in the second position, the valve body 15 is viewed from the side of the second opening P2, and the valve body 15 is a respective of the first opening P1 and the third opening P3. It is provided so that it does not overlap with at least a part. As shown by the dotted line in FIG. 4, when the valve body 15 is in the second position, the valve body 15 is viewed from the second opening P2 side, for example, the first opening P1 and the third opening. It is provided so as not to overlap with P3. The valve body 15 is provided so that the second space S2 is connected to the entire first opening P1 and the third opening P3. When viewed from the second opening P2 side, the angle θ1 formed by the first end portion 151 and the second end portion 152 of the valve body 15 on the outside of the valve body 15 with respect to the rotation axis is, for example, the rotation of the valve body 15. The first virtual line L1 passing through the axis and contacting the first opening P1 and the second virtual line L2 passing through the rotation axis of the valve body 15 and contacting the third opening P3 are equal to the angle θ2 formed with respect to the rotation axis. ..

As shown in FIG. 6, the recess 19 overlaps the entire first opening P1 and the third opening P3 when viewed from the second opening P2 side when the valve body 15 is in the third position. It is provided in. The angle θ3 formed by the third end 191 and the fourth end 192 of the recess 19 with respect to the rotation axis is, for example, equal to the angle θ2.

Each of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B has the valve body 15 in the first position and the valve body 15 in the second position. There are three states, the second state in which the valve body 15 is located, and the third state in which the valve body 15 is in the third position. Each of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B can be independently switched to any of the above three states.

As shown in FIGS. 2 and 3, in the first state, the first space S1 communicating with the first opening P1 and the second opening P2 and being partitioned from the third opening P3 by the valve body 15 , Arranged in each valve chamber 16. In the first state, the valve body 15 does not overlap the first opening P1 in the Z direction. The third surface 18 of the valve body 15 overlaps the entire third opening P3 and closes the third opening P3. The recess 19 of the valve body 15 does not overlap with the first opening P1 and the third opening P3. The third surface 18 is arranged so as to overlap the entire third opening P3 when viewed from the second opening P2 side. The first end portion 151 and the third end portion 191 of the valve body 15 are arranged so as to sandwich the third opening P3 in the circumferential direction when viewed from the second opening P2 side. The recess 19 is arranged so as not to overlap the first opening P1 and the third opening P3 when viewed from the second opening P2 side.

As shown in FIGS. 4 and 5, in the second state, the second space S2 communicating with the first opening P1, the second opening P2, and the third opening P3 is arranged in the valve chamber 16. .. The second space constitutes a branch flow path or a combined flow path. In the second state, the valve body 15 does not overlap the first opening P1 in the Z direction. The valve body 15 does not overlap with at least a part of the third opening P3 in the Z direction. The valve body 15 is arranged at a second position shown by a solid line in FIG. 4, for example. In this case, the third surface 18 is arranged so as to overlap only a part of the third opening P3 when viewed from the second opening P2 side, for example. When viewed from the second opening P2 side, the opening area of the region of the third opening P3 that does not overlap with the valve body 15 is smaller than, for example, the opening area of the first opening P1.

The valve body 15 may be arranged at the second position shown by the dotted line in FIG. 4, for example. In this case, the third surface 18 is arranged so as not to overlap with the third opening P3 when viewed from the second opening P2 side, for example.

As shown in FIGS. 6 and 7, in the third state, the third space S3 communicating with the first opening P1 and the third opening P3 and partitioned from the second opening P2 is the valve body 15. It is arranged in the recess 19. In the third state, the recess 19 of the valve body 15 is arranged so as to overlap the first opening P1 and the third opening P3 in the Z direction.

<Operation of refrigeration cycle device>
The refrigeration cycle device 1000 is switched between a cooling operation state in which the outdoor heat exchanger 3 acts as a condenser and a heating operation state in which the outdoor heat exchanger 3 acts as an evaporator by the four-way valve 2. Further, the refrigeration cycle device 1000 is subjected to a total cooling operation state, a cooling main operation state, a total heating operation state, or a total heating operation state by means of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B. It can be switched to the heating-based operation state.

The refrigeration cycle device 1000 is switched between the first total cooling operation state shown in FIG. 8, the second total cooling operation state shown in FIG. 9, and the third total cooling operation state (not shown) in the total cooling operation state. .. Similarly, in the total heating operation state, the refrigeration cycle device 1000 includes a first total heating operation state shown in FIG. 10, a second total heating operation state shown in FIG. 11, and a third total heating operation state (not shown). Can be switched to.

The first total cooling operation state shown in FIG. 8 is realized when the loads of the first chamber heat exchanger 5A and the second chamber heat exchanger 5B are relatively high. In the first total cooling operation state shown in FIG. 8, each of the first three-way valve 8A and the third three-way valve 8B is in the third state, and each of the second three-way valve 9A and the fourth three-way valve 9B is in the first state. It is said that. In the first total cooling operation state shown in FIG. 8, the refrigerant flows through the refrigerant circuit along the arrow in FIG.

The high-pressure gas-phase refrigerant discharged from the compressor 1 is condensed by the outdoor heat exchanger 3 to become a high-pressure liquid-phase refrigerant or a gas-liquid two-phase refrigerant, and flows out to the first connection pipe 10. The high-pressure liquid-phase refrigerant or gas-liquid two-phase refrigerant that has flowed through the first connection pipe 10 flows into the gas-liquid separator 7 from the inflow port 71. The high-pressure liquid-phase refrigerant flowing out from the second outlet 73 is split in the repeater 300 and reaches the second openings P2 of the second three-way valve 9A and the fourth three-way valve 9B in the first state. It flows through each first space and flows out from each first opening P1 to the fourth connection pipe 13A or the sixth connection pipe 13B. The liquid phase refrigerant flowing through the fourth connecting pipe 13A is decompressed by the first decompression device 4A, then evaporated by the first chamber heat exchanger 5A, and flows out to the third connecting pipe 12A as a low pressure gas phase refrigerant. do. The liquid phase refrigerant flowing through the sixth connection pipe 13B is decompressed by the second decompression device 4B, then evaporates by the second chamber heat exchanger 5B, and flows out to the fifth connection pipe 12B as a low pressure gas phase refrigerant. .. The low-pressure vapor-phase refrigerant flowing through the third connection pipe 12A or the fifth connection pipe 12B reaches the first opening P1 of the first three-way valve 8A and the third three-way valve 8B in the third state, and reaches each third space. After flowing through, it flows out from each third opening P3. The gas phase refrigerant flowing out from each third opening P3 merges in the repeater 300 and flows out to the second connection pipe 11.

As described above, in the first total cooling operation state shown in FIG. 8, the refrigerant discharged from the compressor 1 flows through either the first chamber heat exchanger 5A or the second chamber heat exchanger 5B. , Is sucked into the compressor 1.

The second total cooling operation state shown in FIG. 9 is realized, for example, when only the load of the first chamber heat exchanger 5A falls below a predetermined value. The load of the second chamber heat exchanger 5B in the second total cooling operation state may be lower than the load of the second chamber heat exchanger 5B in the first total cooling operation state.

In the second total cooling operation state shown in FIG. 9, each of the first three-way valve 8A and the third three-way valve 8B is in the third state, the fourth three-way valve 9B is in the first state, and the second three-way valve 9B is in the first state. The valve 9A is in the second state. That is, the second total cooling operation state shown in FIG. 9 is different from the first total cooling operation state shown in FIG. 8 only in that the second three-way valve 9A is in the second state. In the second total cooling operation state shown in FIG. 9, the refrigerant flows through the refrigerant circuit along the arrow in FIG.

The high-pressure liquid-phase refrigerant flowing out from the second outlet 73 is split in the repeater 300, and a part of the high-pressure liquid-phase refrigerant reaches the second opening P2 of the second three-way valve 9A in the second state. The high-pressure liquid-phase refrigerant that has flowed into the second opening P2 of the second three-way valve 9A is further divided in the valve chamber 16 by flowing through the second space. A part of the high-pressure liquid-phase refrigerant that has flowed into the second opening P2 of the second three-way valve 9A flows out from the third opening P3. The liquid phase refrigerant flowing out from the third opening P3 of the second three-way valve 9A is a low-pressure gas phase flowing out from each third opening P3 of the first three-way valve 8A and the third three-way valve 8B in the repeater 300. It merges with the refrigerant and flows out to the second connection pipe 11. The rest of the high-pressure liquid-phase refrigerant that has flowed into the second opening P2 flows out from the first opening P1 to the fourth connection pipe 13A, is depressurized by the first decompression device 4A, and then heat exchanges in the first chamber. Evaporate in vessel 5A.

In the second total cooling operation state shown in FIG. 9, the amount of refrigerant flowing through the first chamber heat exchanger 5A is the first opening P1 and the third opening seen from the second opening P2 side of the second three-way valve 9A. It is controlled as a ratio of each opening area of the portion P3. The above ratio is controlled as the rotation angle of the valve body 15 of the second three-way valve 9A.

Switching between the first total cooling operation state shown in FIG. 8 and the second total cooling operation state shown in FIG. 9, and the valve body 15 of the second three-way valve 9A in the second total cooling operation state shown in FIG. The rotation angle of the above is controlled so that, for example, the evaporation temperature in the first chamber heat exchanger 5A becomes the target evaporation temperature. When it is determined that the evaporation temperature in the first chamber heat exchanger 5A is lower than the target evaporation temperature, the valve body 15 of the second three-way valve 9A rotates from the first position to the second position. The measurement of the evaporation temperature is performed constantly or periodically by, for example, a temperature sensor (not shown) attached to the first chamber heat exchanger 5A. The determination of the evaporation temperature and the control of the rotation angle of the valve body 15 are performed constantly or periodically by, for example, the control unit 310. When switching between the first total cooling operation state and the second total cooling operation state, the drive frequency of the compressor 1 is set to be constant, for example. Here, the constant drive frequency means that the maximum value and the minimum value of the drive frequency are within the range of 95% or more and 105% or less of the average value.

As described above, in the second total cooling operation state shown in FIG. 9, a part of the refrigerant discharged from the compressor 1 uses either the first chamber heat exchanger 5A or the second chamber heat exchanger 5B. It is sucked into the compressor 1 without flowing. Therefore, the flow rate of the refrigerant flowing through the first chamber heat exchanger 5A in the second total cooling operation state shown in FIG. 9 without lowering the drive frequency of the compressor 1 is the first total cooling operation shown in FIG. In this state, the flow rate is less than the flow rate of the refrigerant flowing through the first chamber heat exchanger 5A.

The valve of the second three-way valve 9A in the first total cooling operation state shown in FIG. 8 and the second total cooling operation state shown in FIG. 9 and in the second total cooling operation state shown in FIG. The control of the rotation angle of the body 15 may be performed when the difference between the evaporation temperature of the first chamber heat exchanger 5A and the target evaporation temperature exceeds a predetermined range.

The third total cooling operation state is realized, for example, when only the load of the second chamber heat exchanger 5B falls below a predetermined value. In the third full cooling operation state, each of the first three-way valve 8A and the third three-way valve 8B is in the third state, the second three-way valve 9A is in the first state, and the fourth three-way valve 9B is in the second state. It is considered to be in a state. The flow rate of the refrigerant flowing through the second chamber heat exchanger 5B in the third total cooling operation state is smaller than the flow rate of the refrigerant flowing through the second chamber heat exchanger 5B in the first total cooling operation state shown in FIG.

The first full heating operation state shown in FIG. 10 is realized when the loads of the first indoor heat exchanger 5A and the second indoor heat exchanger 5B are relatively high. In the first full heating operation state shown in FIG. 10, each of the first three-way valve 8A and the third three-way valve 8B is in the first state, and each of the second three-way valve 9A and the fourth three-way valve 9B is in the third state. It is said that. In the first full heating operation state shown in FIG. 10, the refrigerant flows through the refrigerant circuit along the arrow in FIG.

The high-pressure vapor-phase refrigerant discharged from the compressor 1 flows out to the first connection pipe 10 through the third check valve 6C. The high-pressure gas-phase refrigerant that has flowed through the first connection pipe 10 flows into the gas-liquid separator 7 from the inflow port 71. The high-pressure vapor-phase refrigerant flowing out from the first outlet 72 is split in the repeater 300 and reaches the second openings P2 of the first three-way valve 8A and the third three-way valve 8B in the first state. It flows through each first space and flows out from each first opening P1 to the third connection pipe 12A or the fifth connection pipe 12B. The gas-phase refrigerant flowing through the third connection pipe 12A is condensed by the first chamber heat exchanger 5A and then depressurized by the first decompression device 4A, and is decompressed by the first decompression device 4A, and is used as a low-pressure gas-liquid two-phase refrigerant in the fourth connection pipe 13A. Leaked into. The gas-phase refrigerant flowing through the fifth connection pipe 12B is condensed by the second chamber heat exchanger 5B and then depressurized by the second decompression device 4B, and is depressurized by the second decompression device 4B, and is used as a low-pressure gas-liquid two-phase refrigerant in the sixth connection pipe 13B. Leaked into. The low-pressure vapor-phase refrigerant flowing through the fourth connection pipe 13A or the sixth connection pipe 13B reaches the first opening P1 of the second three-way valve 9A and the fourth three-way valve 9B in the third state, and reaches each third space. After flowing through, it flows out from each third opening P3. The gas phase refrigerant flowing out from each third opening P3 merges in the repeater 300 and flows out to the second connection pipe 11.

As described above, in the first full heating operation state shown in FIG. 10, the refrigerant discharged from the compressor 1 flows through either the first chamber heat exchanger 5A or the second chamber heat exchanger 5B. , Is sucked into the compressor 1.

The second total heating operation state shown in FIG. 11 is realized, for example, when only the load of the first indoor heat exchanger 5A falls below a predetermined value. The load of the second indoor heat exchanger 5B in the second full heating operation state shown in FIG. 11 may be lower than that in the first full heating operation state.

In the second full heating operation state shown in FIG. 11, each of the second three-way valve 9A and the fourth three-way valve 9B is in the third state, the third three-way valve 8B is in the first state, and the first three-way valve is in the first state. The valve 8A is in the second state. That is, the second total heating operation state shown in FIG. 11 is different from the first total heating operation state shown in FIG. 10 only in that the first three-way valve 8A is set to the second state. In the second full heating operation state shown in FIG. 11, the refrigerant flows through the refrigerant circuit along the arrow in FIG.

The high-pressure vapor-phase refrigerant flowing out from the first outlet 72 is split in the repeater 300, and a part of it reaches the second opening P2 of the first three-way valve 8A in the second state. The high-pressure vapor-phase refrigerant that has flowed into the second opening P2 of the first three-way valve 8A is further divided in the valve chamber 16 by flowing through the second space. A part of the high-pressure vapor-phase refrigerant that has flowed into the second opening P2 of the first three-way valve 8A flows out from the third opening P3. The gas phase refrigerant flowing out from the third opening P3 of the first three-way valve 8A is a low-pressure gas phase flowing out from each third opening P3 of the second three-way valve 9A and the fourth three-way valve 9B in the repeater 300. It merges with the refrigerant and flows out to the second connection pipe 11. The remaining portion of the high-pressure vapor-phase refrigerant that has flowed into the second opening P2 flows out from the first opening P1 to the third connection pipe 12A and condenses in the first chamber heat exchanger 5A.

In the second full heating operation state shown in FIG. 11, the amount of refrigerant flowing through the first indoor heat exchanger 5A is controlled by the first three-way valve 8A. The amount of refrigerant flowing through the first chamber heat exchanger 5A decreases as the ratio of the opening area of the third opening P3 to the opening area of the first opening P1 of the first three-way valve 8A increases. The above ratio is controlled as the rotation angle of the valve body 15 of the first three-way valve 8A.

Switching between the first total heating operation state shown in FIG. 10 and the second total heating operation state shown in FIG. 11, and the valve body 15 of the first three-way valve 8A in the second total heating operation state shown in FIG. The rotation angle of the above is controlled so that, for example, the condensation temperature in the first chamber heat exchanger 5A becomes the target condensation temperature. When it is determined that the condensation temperature in the first chamber heat exchanger 5A is higher than the target condensation temperature, the valve body 15 of the first three-way valve 8A rotates from the first position to the second position. The measurement of the condensation temperature is performed constantly or periodically by, for example, a temperature sensor (not shown) attached to the first chamber heat exchanger 5A. The determination of the condensation temperature and the control of the rotation angle of the valve body 15 are performed constantly or periodically by, for example, the control unit 310. When switching between the first full heating operation state and the second full heating operation state, the drive frequency of the compressor 1 is set to be constant, for example.

As described above, in the second full heating operation state shown in FIG. 11, a part of the refrigerant discharged from the compressor 1 uses either the first chamber heat exchanger 5A or the second chamber heat exchanger 5B. It is sucked into the compressor 1 without flowing. Therefore, the flow rate of the refrigerant flowing through the first chamber heat exchanger 5A in the second total heating operation state shown in FIG. 11 without lowering the drive frequency of the compressor 1 is the first total heating operation shown in FIG. In this state, the flow rate is less than the flow rate of the refrigerant flowing through the first chamber heat exchanger 5A.

The valve of the first three-way valve 8A in the first total heating operation state shown in FIG. 10 and the second total heating operation state shown in FIG. 11 and in the second total heating operation state shown in FIG. The control of the rotation angle of the body 15 may be performed when the difference between the condensation temperature of the first chamber heat exchanger 5A and the target condensation temperature exceeds a predetermined range.

The third total heating operation state is realized, for example, when only the load of the second indoor heat exchanger 5B falls below a predetermined value. In the third full heating operation state, each of the second three-way valve 9A and the fourth three-way valve 9B is in the third state, the first three-way valve 8A is in the first state, and the third three-way valve 8B is in the second state. It is considered to be in a state. The flow rate of the refrigerant flowing through the second room heat exchanger 5B in the third total heating operation state is smaller than the flow rate of the refrigerant flowing through the second room heat exchanger 5B in the first total heating operation state shown in FIG.

As described above, in the refrigeration cycle apparatus 1000, when the load of either the first chamber heat exchanger 5A or the second chamber heat exchanger 5B is reduced in the first total cooling operation state, the second total cooling operation state or the second is 3 All cooling operation state is realized. Similarly, in the refrigeration cycle apparatus 1000, when the load of either the first indoor heat exchanger 5A or the second indoor heat exchanger 5B is reduced in the first total heating operation state, the second total heating operation state or the third is Full heating operation state is realized. As a result, in the refrigeration cycle device 1000, the flow rate of the refrigerant flowing through the indoor heat exchanger whose load has been reduced can be reduced without lowering the drive frequency of the compressor 1, so that the room in which the indoor unit is arranged is comfortable. The occurrence of chattering in the first check valve 6A, the second check valve 6B, the third check valve 6C, and the fourth check valve 6D is suppressed while preventing the deterioration of the property.

Switching between the total cooling operation state, the cooling main operation state, the total heating operation state, and the heating main operation state can be performed by the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve. It can also be realized by substituting each of 9B with two or more solenoid valves (for example, eight solenoid valves). In this case, the control unit needs to control the movement of each of the eight solenoid valves for the above switching. On the other hand, in the refrigeration cycle device 1000, the above switching can be performed by controlling only the movement of each valve body of the four three-way valves by the control unit 310. Therefore, the number of ports of the control unit 310 of the refrigeration cycle device 1000 is reduced as compared with the refrigeration cycle device having a plurality of solenoid valves instead of the three-way valves.

In the refrigeration cycle device 1000, the valve body 15 may be arranged so as not to overlap the first opening P1 and the third opening P3 when viewed from the second opening P2 side. As shown by the dotted line in FIG. 4, when the valve body 15 is arranged so as not to overlap the first opening P1 and the third opening P3 when viewed from the second opening P2 side in the second state. As shown by the solid line in FIG. 4, the valve body 15 is arranged so as to overlap a part of the third opening P3 when viewed from the second opening P2 side in the second state. The flow rate of the refrigerant flowing through the indoor heat exchanger 5A is further reduced. From a different point of view, in the former case, the difference between the flow rate of the refrigerant flowing through the first chamber heat exchanger 5A and the flow rate of the refrigerant flowing through the second chamber heat exchanger 5B is larger than in the latter case. .. Therefore, in the former case, even when the loads of the first chamber heat exchanger 5A and the second chamber heat exchanger 5B are relatively large, the first chamber heat exchanger 5A and the second chamber heat exchanger 5B The flow rate of the refrigerant flowing through each can be appropriately set according to each load.

The refrigeration cycle device 1000 is switched between the first cooling-based operating state shown in FIG. 12 and the second cooling-based operating state (not shown) in the cooling-based operating state. Similarly, the refrigeration cycle device 1000 is switched between the first heating-based operating state shown in FIG. 13 and the second heating-based operating state (not shown) in the heating-based operating state.

The first cooling-based operating state shown in FIG. 12 is realized when the load of the first chamber heat exchanger 5A acting as an evaporator is higher than the load of the second chamber heat exchanger 5B acting as a condenser. NS. In the first cooling main operating state, each of the first three-way valve 8A and the fourth three-way valve 9B is in the third state, the third three-way valve 8B is in the first state, and the second three-way valve 9A is in the second state. It is considered to be in a state. The second cooling-based operating state is realized when the load of the second chamber heat exchanger 5B acting as an evaporator is higher than the load of the first chamber heat exchanger 5A acting as a condenser. In the second cooling main operating state, each of the second three-way valve 9A and the third three-way valve 8B is in the third state, the first three-way valve 8A is in the first state, and the fourth three-way valve 9B is in the second state. It is considered to be in a state.

The first heating-based operating state shown in FIG. 13 is realized when the load of the first chamber heat exchanger 5A acting as a condenser is higher than the load of the second chamber heat exchanger 5B acting as an evaporator. NS. In the first heating main operating state, the third three-way valve 8B is in the third state, the first three-way valve 8A and the fourth three-way valve 9B are in the first state, and the second three-way valve 9A is in the second state. Will be done. The second heating-based operating state is realized when the load of the second chamber heat exchanger 5B acting as a condenser is higher than the load of the first chamber heat exchanger 5A acting as an evaporator. In the second heating main operating state, the first three-way valve 8A is in the third state, the second three-way valve 9A and the third three-way valve 8B are in the first state, and the fourth three-way valve 9B is in the second state. Will be done.

<Modification example>
The refrigeration cycle apparatus 1000 may include three or more indoor heat exchangers and a three-way valve that is a multiple of the number of the indoor heat exchangers. The refrigeration cycle device 1000 is, for example, from a third chamber heat exchanger connected in parallel with the first chamber heat exchanger 5A and the second chamber heat exchanger 5B, and from the third chamber heat exchanger in the above cooling operation state. The fifth three-way valve, which is arranged downstream and upstream of the third chamber heat exchanger in the heating operation state, and is arranged upstream of the third chamber heat exchanger in the cooling operation state. Moreover, the sixth three-way valve arranged downstream from the third chamber heat exchanger in the heating operation state may be further provided. The fifth three-way valve is connected in parallel with the first three-way valve 8A and the third three-way valve 8B. The sixth three-way valve is connected in parallel with the second three-way valve 9A and the fourth three-way valve 9B.

As shown in FIGS. 14 to 16, in each of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B, the first opening P1 is the third opening. It may be arranged side by side with a space between the portion P3 and the X direction as the first direction. In this case, the valve bodies 15 of the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B are provided so as to reciprocate along the X direction. The third surface 18 of each valve body 15 is arranged side by side with the recess 19 in the X direction. The distance in the X direction between the first end portion 151 and the third end portion 191 is wider than the distance in the X direction between the second end portion 152 and the fourth end portion 192.

The fourth surface 20 of the valve body 15 is provided so as to slide with, for example, the second surface 14B of the valve seat 14. The second opening P2 is arranged so as to face, for example, the first opening P1. The fourth surface 20 of the valve body 15 may be provided so as to face, for example, the second surface 14B of the valve seat 14 at a distance. In this case, each valve seat 14 is provided with a holding portion for holding a state in which the first surface 14A of the valve seat 14 and the third surface 18 of the valve body 15 are in contact with each other.

As shown in FIGS. 14 to 16, the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B as described above are also shown in FIGS. 2 to 7. 1 As with the three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B, three states of the first state, the second state, and the third state can be taken. Therefore, the refrigeration cycle apparatus 1000 including the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B shown in FIGS. 14 to 16 is also shown in FIGS. 2 to 7. The same effect as that of the refrigeration cycle device 1000 including the first three-way valve 8A, the second three-way valve 9A, the third three-way valve 8B, and the fourth three-way valve 9B can be obtained.

The refrigeration cycle device 1000 may further include a device for preventing the liquid from returning to the compressor 1. Such a device is, for example, an accumulator or a heat exchanger that exchanges heat between the refrigerant discharged from the compressor 1 and the refrigerant sucked into the compressor 1.

Although the embodiment of the present disclosure has been described as described above, it is also possible to modify the above-described embodiment in various ways. Moreover, the scope of the present disclosure is not limited to the above-described embodiment. The scope of the present disclosure is indicated by the claims and is intended to include all modifications within the meaning and scope equivalent to the claims.

1 Compressor, 2 4-way valve, 3 Outdoor heat exchanger, 4A 1st decompression device, 4B 2nd decompression device, 5A 1st indoor heat exchanger, 5B 2nd indoor heat exchanger, 6A 1st check valve, 6B 2nd check valve, 6C 3rd check valve, 6D 4th check valve, 7 gas-liquid separator, 8A 1st three-way valve, 8B 3rd three-way valve, 9A 2nd three-way valve, 9B 4th three-way valve, 10 1st connection pipe, 11 2nd connection pipe, 12A 3rd connection pipe, 12B 5th connection pipe, 13A 4th connection pipe, 13B 6th connection pipe, 14 valve seat, 14A 1st surface, 14B 2nd surface, 15 valve body, 16 valve chamber, 17 gear, 18 third surface, 19 recess, 20 fourth surface, 71 inlet, 72 first outlet, 73 second outlet, 100 outdoor unit, 151 first end, 152 2nd end, 191 3rd end, 192 4th end, 200A 1st indoor unit, 200B 2nd indoor unit, 300 repeater, 310 control unit, 1000 refrigeration cycle device, L1 1st virtual line, L2 2nd virtual line, P1 1st opening, P2 2nd opening, P3 3rd opening, S1 1st space, S2 2nd space, S3 3rd space.

Claims

From the compressor, flow path switching unit, outdoor heat exchanger, decompression device, first indoor heat exchanger, first connection pipe through which the refrigerant flowing into the first indoor heat exchanger flows, and the first indoor heat exchanger. It includes a second connection pipe through which the outflowing refrigerant flows, and is equipped with a refrigerant circuit in which the refrigerant circulates.
The flow path switching unit switches between a cooling operation state in which the outdoor heat exchanger acts as a condenser and a heating operation state in which the outdoor heat exchanger acts as an evaporator.
The refrigerant circuit
A first three-way valve arranged downstream of the first indoor heat exchanger in the cooling operation state and upstream of the first indoor heat exchanger in the heating operation state.
Further including a second three-way valve arranged upstream of the first chamber heat exchanger in the cooling operation state and downstream of the first chamber heat exchanger in the heating operation state.
Each of the first three-way valve and the second three-way valve has a valve seat including a valve chamber and a first opening, a second opening, and a third opening connected to the valve chamber, and the valve chamber. Includes a valve body that moves between the first, second, and third positions of the
The first opening of each of the first three-way valve and the second three-way valve is connected to one end or the other end of the first chamber heat exchanger in the refrigerant circuit.
The second opening of each of the first three-way valve and the second three-way valve is connected to the first connection pipe.
The third opening of each of the first three-way valve and the second three-way valve is connected to the second connection pipe.
Each of the first three-way valve and the second three-way valve has a first state in which the valve body is in the first position, a second state in which the valve body is in the second position, and the valve body. Switched independently of each other to any of the third states in the third position.
In the first state, a first space communicating with the first opening and the second opening and partitioned from the third opening is arranged in the valve chamber.
In the second state, the first opening, the second opening, and the second space communicating with the third opening are arranged in the valve chamber.
In the third state, a refrigeration cycle device in which a third space communicating with the first opening and the third opening and partitioned from the second opening is arranged in the valve chamber.
The valve seat has a first surface facing the valve chamber and having the first opening and the third opening formed, and a second surface having the second opening formed. death,
The first opening is arranged side by side with a distance from the third opening in the first direction.
The valve body has a third surface that slides on the first surface, and a recess that is arranged side by side with the third surface in the first direction and is recessed with respect to the third surface. death,
In the first state, the third surface is arranged so as to overlap the third opening when viewed from the second opening side, and the recess is formed with the first opening and the third opening. Arranged so that they do not overlap,
The refrigeration cycle apparatus according to claim 1, wherein in the third state, the recess is arranged so as to overlap the first opening and the third opening, and the third space is formed in the recess.
The second surface faces the first surface with the valve body interposed therebetween.
The valve body is provided so as to rotate about a rotation axis extending along a second direction.
The refrigeration cycle apparatus according to claim 2, wherein the first direction is a circumferential direction with respect to the rotation axis.
The refrigeration cycle device according to claim 3, wherein the valve body is provided so that the second space is connected to the entire first opening and the third opening.
The refrigerant circuit
A second chamber heat exchanger connected in parallel with the first chamber heat exchanger to the first connecting pipe and the second connecting pipe.
A third three-way valve arranged downstream of the first chamber heat exchanger in the cooling operation state and upstream of the second chamber heat exchanger in the heating operation state.
Further including a fourth three-way valve located upstream of the first chamber heat exchanger in the cooling operating state and downstream of the second chamber heat exchanger in the heating operating state.
The third three-way valve and the fourth three-way valve have the same configuration as the first three-way valve and the second three-way valve, and any of the first state, the second state, and the third state. Can be switched independently of each other
In the cooling operation state where the load of the first chamber heat exchanger is lower than the load of the second chamber heat exchanger, the first three-way valve and the third three-way valve are set to the third state, and the second The three-way valve is in the second state, the fourth three-way valve is in the first state, and so on.
In the heating operation state in which the load of the first chamber heat exchanger is lower than the load of the second chamber heat exchanger, the second three-way valve and the fourth three-way valve are set to the third state, and the first The refrigeration cycle apparatus according to any one of claims 1 to 4, wherein the three-way valve is in the second state and the third three-way valve is in the first state.
The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the drive frequency of the compressor is constant when switching between the first state and the second state is performed.
The refrigerant circuit
A first check valve that is arranged in the refrigerant flow path between the outdoor heat exchanger and the first connection pipe and allows only the refrigerant flowing from the outdoor heat exchanger to the first connection pipe flows.
A second check valve that is arranged in the refrigerant flow path between the outdoor heat exchanger and the second connection pipe and allows only the refrigerant flowing from the second connection pipe to the outdoor heat exchanger to flow.
A third check valve that is arranged in the refrigerant flow path between the flow path switching portion and the first connection pipe and allows only the refrigerant flowing from the flow path switching portion to the first connection pipe flows.
A fourth check valve which is arranged in the refrigerant flow path between the flow path switching portion and the second connection pipe and allows only the refrigerant flowing from the second connection pipe to the flow path switching portion is further included. , The refrigeration cycle apparatus according to any one of claims 1 to 6.
The refrigerant circuit further includes a gas-liquid separator.
The gas-liquid separator includes an inflow port connected to the first connection pipe, a first outflow port connected to the second opening of the first three-way valve and flowing out the gas phase refrigerant, and the first outlet. 2. The refrigeration cycle apparatus according to any one of claims 1 to 7, which is connected to the second opening of the three-way valve and has a second outlet for flowing out the liquid phase refrigerant.
The first connection pipe and the second connection pipe accommodate the compressor, the flow path switching portion, the outdoor unit accommodating the outdoor heat exchanger, and the first three-way valve and the second three-way valve. The refrigeration cycle apparatus according to any one of claims 1 to 8, which is arranged between the repeater and the repeater.