WO2022224406A1

WO2022224406A1 - Refrigeration cycle apparatur and indoor unit

Info

Publication number: WO2022224406A1
Application number: PCT/JP2021/016303
Authority: WO
Inventors: 真哉東井上
Original assignee: 三菱電機株式会社
Priority date: 2021-04-22
Filing date: 2021-04-22
Publication date: 2022-10-27
Also published as: CN117157493A; US20240133576A1; EP4328512A4; JPWO2022224406A1; EP4328512A1; JP7466764B2

Abstract

In the refrigeration cycle apparatus according to the present disclosure, an indoor unit comprises: a first heat exchanger that is provided with a first suction port communicating with the inside of a room and a second suction port communicating with the outside of the room, and that is disposed in a first air passage joining the first suction port and the second suction port; a second heat exchanger that is disposed in a second air passage joining the second suction port and a blow-out port, and that is connected to the first heat exchanger so as to be positioned downstream of the first heat exchanger when the refrigeration cycle apparatus is in heating operation; a first damper capable of adjusting the amount of air flowing into the second air passage from the first air passage; and a second damper that is provided to the second suction port and that is capable of adjusting the amount of air sucked in from the second suction port.

Description

Refrigeration cycle device and indoor unit

The present disclosure relates to a refrigeration cycle device and an indoor unit.

In conventional refrigeration cycle devices, the air is cooled or heated by heat exchange between the room air and the refrigerant flowing through the heat exchanger. Also, in recent years, there is a refrigeration cycle device equipped with a technology for taking in outside air into an indoor unit and performing cooling and heating while ventilating. (See Patent Document 1, for example).

Japanese Patent Laid-Open No. 11-257793

However, in the refrigeration cycle apparatus disclosed in Patent Document 1, since the indoor unit is provided with a heat exchanger exclusively for ventilation, the size of the heat exchanger that can be used for cooling and heating without ventilation is limited. , the efficiency of the refrigeration cycle apparatus may be lowered.

This disclosure was made to solve such problems. It is an object of the present invention to provide a refrigerating cycle device for cooling and heating, in which the presence or absence of ventilation can be set, and a decrease in efficiency can be suppressed when ventilation is not performed.

In the refrigeration cycle apparatus according to the present disclosure, the indoor unit is provided with a first suction port that communicates with the room and a second suction port that communicates with the outside, and the first suction port and the air outlet are connected. A first heat exchange section arranged in the first air passage and a second air passage connecting a second suction port and an air outlet, and the first heat exchange portion is arranged in the refrigeration cycle device during heating operation. a second heat exchange section connected to the first heat exchange section so as to be located downstream of the section; and a first damper capable of adjusting the amount of air flowing from the first air passage to the second air passage. and a second damper provided at the second suction port and capable of adjusting the amount of air sucked from the second suction port.

According to the refrigeration cycle device of the present disclosure, it is possible to set the presence or absence of ventilation, and compared with the indoor heat exchanger installed in the conventional refrigeration cycle device, it is possible to exhibit the same performance even without ventilation. . As a result, a decrease in efficiency of the refrigeration cycle device can be suppressed regardless of the usage conditions.

1 is a diagram showing the configuration of a refrigeration cycle apparatus according to Embodiment 1; FIG. 4 is a diagram showing the operation of the indoor unit according to Embodiment 1. FIG. 4 is a diagram showing the state of the indoor heat exchanger during heating operation in Embodiment 1. FIG. 4 is a diagram showing another configuration of the indoor unit according to Embodiment 1. FIG. 4A and 4B are diagrams showing the structure, operation, and air flow of the indoor unit in Embodiment 1. FIG. FIG. 8 is a diagram showing the structure, operation, and air flow of an indoor unit in Example 2; FIG. 10 is a diagram showing the structure, operation, and airflow of an indoor unit in Example 3; FIG. 11 is a diagram showing operating means of a second damper in Example 3; FIG. 5 is a diagram showing a modification of the indoor unit in Embodiment 1; FIG. 10 is a diagram showing a modification of the indoor unit in Embodiment 2;

A mode for carrying out the present disclosure will be described with reference to the attached drawings. In each figure, the same or corresponding parts are denoted by the same reference numerals, and overlapping descriptions are appropriately simplified or omitted. It should be noted that the following embodiments do not limit the scope of the present disclosure.

Embodiment 1.
FIG. 1 is a diagram showing the configuration of a refrigeration cycle apparatus 100 according to this embodiment. A refrigeration cycle device 100 includes a compressor 1 , a four-way valve 2 , an indoor unit 3 , an expansion valve 9 and an outdoor heat exchanger 10 . Further, in FIG. 1 , the indoor unit 3 accommodates a first indoor heat exchange section 4 , a second indoor heat exchange section 5 and a first indoor fan 6 . The outdoor heat exchanger 10 is housed in an outdoor unit (not shown), and the outdoor unit also houses an outdoor fan.

Furthermore, the refrigeration cycle device 100 includes a control device 50 . The control device 50 commands the compressor 1, the four-way valve 2, the first air blowing means 6, the expansion valve 9, the first damper 11 and the second damper 12 to be described later, and the outdoor blower (not shown). to control each action.

The compressor 1, the four-way valve 2, the first indoor heat exchange section 4, the second indoor heat exchange section 5, the expansion valve 9, and the outdoor heat exchanger 10 are connected by piping to form a refrigerant circuit. Configure. A refrigerant such as R32 (difluoromethane) circulates in the refrigerant circuit. The type of refrigerant enclosed in refrigeration cycle device 100 is not limited.

In FIG. 1, the refrigerant flows in the direction indicated by the dashed arrow in cooling operation. That is, the refrigerant discharged from the compressor 1 is condensed in the outdoor heat exchanger 10 , decompressed in the expansion valve 9 , and evaporated in the second indoor heat exchange section 5 and the first indoor heat exchange section 4 . Evaporated refrigerant returns to the compressor 1 .

On the other hand, in heating operation, the refrigerant flows in the direction indicated by the solid arrow. That is, the refrigerant discharged from the compressor 1 is condensed in the first indoor heat exchange section 4 and the second indoor heat exchange section 5 , decompressed in the expansion valve 9 , and evaporated in the outdoor heat exchanger 10 . Evaporated refrigerant returns to the compressor 1 . Switching between the cooling operation and the heating operation is performed by changing the connection of the refrigerant circuit with the four-way valve 2 .

The compressor 1 is, for example, a rotary compressor. The capacity, rated frequency, and the like of the compressor 1 are determined by the type of refrigerant sealed in the refrigerant circuit, the capacity of the refrigeration cycle device 100, and the like. The compressor 1 may be a piston type or scroll type compressor. Further, the compressor 1 may be operated at the rated frequency by the control device 50, or the frequency may be variably controlled by an inverter mounted on the control device 50. FIG.

The four-way valve 2 has a function of switching the flow path, and switches the flow path depending on whether the refrigeration cycle device 100 performs cooling operation or heating operation. During cooling operation, the four-way valve 2 connects the outlet of the compressor 1 and the outdoor heat exchanger 10 and connects the first indoor heat exchanger 4 and the suction port of the compressor 1 . On the other hand, when performing heating operation, the four-way valve 2 connects the discharge port of the compressor 1 and the first indoor heat exchange section 4 , and connects the outdoor heat exchange 10 and the suction port of the compressor 1 . Connection of the four-way valve 2 is switched by the controller 50 .

The indoor unit 3 accommodates a first indoor heat exchange section 4, a second indoor heat exchange section 5, and a first indoor fan 6. The first indoor heat exchange section 4 and the second indoor heat exchange section 5 may be the same indoor heat exchanger, or may be separate indoor heat exchangers. The structural relationship between the first indoor heat exchange section 4 and the second indoor heat exchange section 5 is the following two points. The first point is that the first indoor heat exchange unit 4 is positioned upstream in the refrigerant flow when the refrigeration cycle device 100 performs heating operation, and the second indoor heat exchange unit 5 is positioned upstream during the heating operation. It is positioned downstream of one indoor heat exchange section 4 . The second point is that the indoor air always flows through the first indoor heat exchange section 4, but the outside air or the indoor air flows through the second indoor heat exchange section 5, as will be described later.

The first indoor heat exchange section 4 and the second indoor heat exchange section 5 are, for example, fin-tube heat exchangers composed of copper pipes and aluminum fins fixed to the copper pipes. Coolant flows inside the copper tube, and the heat of the coolant is transferred to the fins. Thereby, heat exchange is performed between the air flowing between the fins and the refrigerant. In general, in a finned-tube heat exchanger, refrigerant flows through many branched copper pipes (hereinafter referred to as paths). It may be the same as or different from the heat exchange section 5 . Further, the density and shape of the fins may be the same or different between the first indoor heat exchange section 4 and the second indoor heat exchange section 5 . Considering the volumes of the first heat exchange section 4 and the second heat exchange section 5 , the volume of the first heat exchange section 4 is larger than the volume of the second heat exchange section 5 . As will be described later, when the refrigeration cycle device 100 performs a heating operation, a large amount of refrigerant in a gas state and a gas-liquid two-phase state flows through the first indoor heat exchange section 4a, and a liquid refrigerant flows through the second indoor heat exchange section 4b. A lot of refrigerant in the state flows. In the heat exchanger of the refrigeration cycle, the volume occupied by the refrigerant in the gas state and the gas-liquid two-phase state is generally large. be.

The first indoor heat exchange section 4 and the second indoor heat exchange section 5 are connected by copper pipes. The first indoor heat exchange section 4 and the second indoor heat exchange section 5 may be connected in any way. For example, if the number of paths of the first indoor heat exchange section 4 and the number of paths of the second indoor heat exchange section 5 are the same, the respective paths may be connected. Alternatively, when the number of paths in the first indoor heat exchange section 4 is greater than the number of paths in the second indoor heat exchange section 5, some of the paths in the first indoor heat exchange section 4 are merged to form the second You may make it join the path|path of the indoor heat exchange part 5. FIG.

The first indoor fan 6 is, for example, a cross-flow fan provided inside the indoor unit 3. The first indoor fan 6 generates an airflow for blowing out the air temperature-controlled by the first indoor heat exchange section 4 and the second indoor heat exchange section 5 from the indoor unit 3 . The first indoor fan 6 is controlled by the controller 50 . As the first indoor blower 6, not only a cross-flow fan but also any means such as a propeller fan or a sirocco fan can be used.

Also, the indoor unit 3 is formed with a first intake port 13 for sucking indoor air, a second intake port 14 for sucking outside air, and a blowout port 15 for blowing out temperature-controlled air. Here, the second suction port 14 sucks outside air from, for example, a ventilation hole provided in the wall of the room or a duct connected to the outside.

The indoor air sucked into the indoor unit 3 through the first inlet 13 passes through the first indoor heat exchange section 4 and is blown out through the outlet 15 . On the other hand, outside air sucked into the indoor unit 3 through the second inlet 14 passes through the second indoor heat exchange section 5 and is blown out from the outlet 15 . Here, the passage through which the indoor air flows, that is, the route connecting the first suction port 13 and the discharge port 15 is referred to as the first air passage 7 . Similarly, an air passage through which outside air flows, that is, a route connecting the second suction port 14 and the air outlet 15 is referred to as a second air passage 8 .

FIGS. 2(a) to 2(d) are diagrams showing the states of the first damper 11 and the second damper 12 and the air flow in the first air passage 7 and the second air passage 8. FIG. Here, the first damper 11 is attached in the first air passage at a position where the amount of indoor air branched from the first air passage 7 and flowing into the second air passage can be adjusted. On the other hand, the second damper 12 is attached to a position such as the vicinity of the second suction port 14 where the amount of outside air sucked from the suction port 14 can be adjusted.

Here, an example of the mounting position of the first damper 11 will be described in more detail. As shown in FIGS. 2(a) and 2(b), a partition wall 18 may be provided inside the indoor unit 3 to separate the first air passage 7 and the second air passage 8 from each other. In this case, a part of the partition wall 18 has a hole communicating between the first air passage 7 and the second air passage 8, and the first damper 11 is attached at a position capable of opening and closing the hole. By attaching the first damper 11 in this way, the first damper 11 inhibits the indoor air flowing through the first air passage 7 from flowing to the second heat exchange section 5, or Air can be arranged to flow to the second heat exchange section 5 .

In the above description, an example in which the partition wall 18 is provided inside the indoor unit 3 is shown. good. The purpose of providing the partition wall 18 is to prevent indoor air from flowing into the second heat exchange section 5 when the first damper 11 is in the closed state. Therefore, the structure of the partition wall 18 is not limited to the example in which the first air passage 7 and the second air passage 8 are separated from each other as described above and a part of the partition wall 18 has a hole communicating between the two air passages.

From here on, the air flow inside the indoor unit 3 will be explained in more detail. In FIG. 2A, the first damper 11 is closed and the second damper 12 is open. In this case, the indoor air sucked from the first suction port 13 flows into the first indoor heat exchange section 4 from the first air passage 7 . Outside air sucked from the second suction port 14 flows into the second indoor heat exchange section 5 from the second air passage 8 .

On the other hand, in FIG. 2(b), the first damper 11 is open and the second damper 12 is closed. In this case, the indoor air sucked from the first suction port 13 flows through the first air passage 7 . Furthermore, since the first damper 11 is in an open state, part of the sucked indoor air branches in the first air passage 7 and also flows into the second air passage 8 . In this case, indoor air flows into both the first indoor heat exchange section 4 and the second indoor heat exchange section 5 .

On the other hand, in FIG. 2(c), the first damper 11 is in the closed state and the second damper 12 is in the half-open state. In this case, the indoor air sucked from the first suction port 13 flows through the first air passage 7 . Outside air sucked from the second suction port 14 flows through the second air passage 8 . The second damper 12 is in a half-open state, and the opening area of the second suction port 14 is smaller than that in FIG. 2(a). Therefore, the amount of outside air sucked from the second suction port 14 is smaller than in the case of FIG. 2(a).

On the other hand, in FIG. 2(d), both the first damper 11 and the second damper 12 are in a half-open state. In this case, the room air sucked from the first suction port 13 passes through the first air passage 7 . Since the first damper 11 is in a half-open state, part of the sucked indoor air flows into the second air passage 8 . Also, the outside air sucked from the second suction port 14 and part of the indoor air flow through the second air passage 8 .

The expansion valve 9 is, for example, an electromagnetic valve whose opening can be controlled. The expansion valve 9 decompresses the high-pressure refrigerant that has flowed into it to a low-pressure refrigerant. The degree of opening of the solenoid valve is controlled by the controller 50 .

The outdoor heat exchanger 10 is, for example, a fin-tube heat exchanger. Although one outdoor heat exchanger 10 is illustrated in FIG. 1, for example, the number of passes may be changed in the middle, or the density and shape of the fins may be changed.

The control device 50 is composed of, for example, a CPU (Central Processing Unit), a storage medium such as a ROM (Read Only Memory) storing a control program, a working memory such as a RAM (Random Access Memory), and a communication circuit. The control device 50 operates the compressor 1, the four-way valve 2, the first air blowing means 6, the expansion valve 9, the first damper 11 according to a pre-stored operation program or a signal input by the user of the refrigeration cycle apparatus. , the second damper 12 and the outdoor fan to control their operations.

Next, the operation and effects of this embodiment will be described. First, the heating operation in which the effect of the refrigeration cycle device 100 of the present disclosure is particularly large will be described.

Also, in the following description, the first damper 11 and the second damper 12 automatically operate by detecting the indoor environment with a sensor or the like. In this case, the state of the first damper 11 and the second damper 12 in FIGS. According to.

Note that this does not limit the configuration of the refrigeration cycle device 100 in the present disclosure, and the first damper 11 and the second damper 12 are operated according to a signal input by the user of the refrigeration cycle device 100 by means of a remote control or the like. It may be operated or may be manually operated by the user.

First, consider a situation where the outside air temperature is lower than the indoor air temperature and the indoor air is polluted. In this case, the first damper 11 is closed and the second damper 12 is open as shown in FIG. 2(a). In this case, indoor air flows through the first air passage 7 and the first indoor heat exchange section 4 , and outside air flows through the second air passage 8 and the second indoor heat exchange section 5 .

In this case, outside air is supplied to the room, so indoor air pollution is alleviated. The polluted air in the room is exhausted to the outside through windows, ventilation openings, or gaps provided in the room.

At this time, high-temperature indoor air flows through the first indoor heat exchange section 4 and low-temperature outdoor air flows through the second indoor heat exchange section 5 . FIG. 3 is a diagram showing the states of the first indoor heat exchange section 4 and the second indoor heat exchange section 5. As shown in FIG. In addition, in FIG. 3, the states of the first indoor heat exchange section 4 and the second indoor heat exchange section 5 in FIG. 2(a) are indicated by solid lines. In FIG. 3 , the high-temperature, high-pressure gas refrigerant compressed by the compressor 1 flows into the first indoor heat exchange section 4 . The high-temperature, high-pressure gas refrigerant exchanges heat with the room air to become a gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant further exchanges heat with the room air to become a liquid refrigerant.

The liquid refrigerant flows into the second indoor heat exchange section 5 . Here, since the temperature of the outside air is lower than the temperature of the indoor air, the temperature difference between the refrigerant and the outside air increases in the second indoor heat exchange section 5, increasing the amount of heat exchange. The refrigerant that has become a supercooled liquid due to heat exchange flows out from the second indoor heat exchange section 5 .

Here, the difference between the state of the first indoor heat exchange unit 4 and the second indoor heat exchange unit 5 in the present disclosure and the indoor heat exchanger of a conventional refrigeration cycle device that does not take outside air into the indoor unit will be described. do. In FIG. 3, the state of the conventional indoor heat exchanger is indicated by dotted lines. In a conventional heat exchanger, heat is exchanged between indoor air having a high temperature and the refrigerant even in a region where the refrigerant is liquid. That is, since the temperature difference between the air and the refrigerant is small, the amount of heat exchange is reduced.

In this case, in order to secure the amount of heat exchanged in the liquid region, the supercooled region inside the heat exchanger expands and the gas-liquid two-phase region shrinks. In general, the in-tube heat transfer coefficient in a heat exchanger is higher in the gas-liquid two-phase region than in the supercooled region. Therefore, in a conventional heat exchanger with a large subcooling region, the efficiency of the heat exchanger decreases and the pressure inside the heat exchanger increases.

On the other hand, in the case of the first indoor heat exchange unit 4 and the second indoor heat exchange unit 5 of the present disclosure indicated by solid lines, the temperature difference between the refrigerant and the outside air is large in the second indoor heat exchange unit 5, A sufficient amount of heat exchange can be secured even in the supercooled region. As a result, the gas-liquid two-phase region in the heat exchanger is larger than that of conventional heat exchangers, and the efficiency of the heat exchanger is good. This results in a lower pressure in the heat exchanger compared to conventional heat exchangers. When the pressure in the heat exchanger decreases, the high-to-low pressure ratio of the refrigerating cycle formed in the refrigerating cycle device 100, that is, the compression ratio in the compressor 1 decreases, so the efficiency of the compressor 1 improves, leading to energy saving. Furthermore, since the supercooled liquid area becomes smaller, the amount of refrigerant charged in the entire refrigeration cycle apparatus 100 is reduced.

In addition, in the second indoor heat exchange section 5, where the temperature difference between the refrigerant and the outside air is large, the amount of heat exchanged between the refrigerant and the outside air is large, so the temperature of the outside air flowing into the indoor unit can be rapidly raised. As a result, problems such as a decrease in heating capacity and a decrease in blow-out temperature are less likely to occur despite the fact that ventilation is performed by allowing the outside air to flow into the room.

Next, consider a situation where the indoor air is not polluted. In this case, the second damper 12 is closed and the first damper 11 is open as shown in FIG. 2(b). In this case, the indoor air flows through the first indoor heat exchange section 4 and the second indoor heat exchange section 5 . At this time, the states of the first indoor heat exchange unit 4 and the second indoor heat exchange unit 5 are the same as those of a conventional heat exchanger that does not take in outside air into the indoor unit, so description thereof will be omitted.

Next, I will explain the case where the indoor air is polluted, but the degree is light. In this case, the second damper 12 is in a half-open state and the first damper 11 is in a closed state, as shown in FIG. 2(c). In this case, outside air flows through the second air passage 8 and the second indoor heat exchange section 5, but the amount of the outside air is compared to the amount of outside air when the second damper 12 is open as shown in FIG. 2(a). less. This is because the second damper 12 is in a half-open state and acts as a ventilation resistance.

In the state shown in FIG. 2(c), the indoor ventilation is performed more slowly than in the case shown in FIG. 2(a). Even in this case, the temperature difference between the refrigerant and the outside air increases in the second indoor heat exchange section 5, and the efficiency of the entire heat exchanger improves as shown in FIG. In addition, since the amount of outside air is small, problems such as a decrease in heating capacity and a decrease in blowout temperature are less likely to occur.

Furthermore, when the temperature of the outside air is higher than the temperature of the room air, the first damper 11 may be in a half-open state as shown in FIG. 2(d). In this case, part of the room air sucked from the first suction port 13 flows into the second air passage 8 . In the second air passage 8, the indoor air and the outside air sucked from the second suction port 14 are mixed. At this time, the temperature of the indoor air is lower than the temperature of the outside air, so the temperature of the mixed air is lower than the temperature of the outside air. The mixed air flows into the second indoor heat exchange section 5 .

When the temperature of the outside air is high, if the outside air is allowed to flow into the second indoor heat exchange section 5, the amount of heat exchange is reduced because the temperature difference between the refrigerant and the outside air is small. However, by mixing the indoor air and the outdoor air as shown in FIG. Thereby, ventilation can be performed while suppressing a decrease in heat exchange amount.

The operation of the refrigeration cycle device 100 has been described above. However, the examples shown in FIGS. 2(a) to 2(d) do not limit the operation of the refrigeration cycle apparatus 100, and the refrigeration cycle apparatus 100 is shown in FIGS. 2(a) to 2(d). Other operations can also be performed. For example, both the first damper 11 and the second damper 12 may be opened. In this case, even when the temperature of the outside air is high, it is possible to reduce the decrease in the heat exchange amount of the second indoor heat exchange section 5 after increasing the ventilation amount.

2(a) to 2(d), the first damper 11 and the second damper 12 are either in an open state, a closed state, or a half-open state. The damper 12 can be in an intermediate state between the open state and the half-open state, and an intermediate state between the closed state and the half-open state. In this way, by enabling fine setting of the opening degrees of the first damper 11 and the second damper 12, it is possible to adjust the amount of ventilation according to the indoor conditions and optimize the efficiency of the heat exchanger. .

In addition, although the case of the heating operation has been described above, the refrigeration cycle device 100 can also perform the cooling operation. In that case, consider a situation in which the temperature of the outside air is higher than the temperature of the indoor air, and the indoor air is polluted. In this case, as shown in FIG. 2A, the second damper 12 is in an open state and the first damper 11 is in a closed state. Outside air flows through the exchange portion 5 .

At this time, a low-temperature gas-liquid two-phase refrigerant decompressed by the expansion valve 9 is flowing through the second indoor heat exchange section 5 . When outside air having a high temperature flows into the second indoor heat exchange section 5, the temperature difference between the refrigerant and the outside air increases, so the amount of heat exchange increases. At this time, the outside air, which has a high temperature, rapidly cools down due to heat exchange. Therefore, the refrigerating cycle device 100 can ventilate with outside air while preventing a decrease in cooling capacity and an increase in blowing temperature.

The refrigeration cycle device 100 switches the states of the first damper 11 and the second damper 12 according to the contamination status of the indoor air and the temperatures of the outside air and the indoor air even during the cooling operation. As a result, an appropriate amount of ventilation can be performed while maintaining the cooling capacity and the efficiency of the refrigeration cycle apparatus 100 in various situations.

As described above, in the present embodiment, the refrigeration cycle device 100 operates the first damper 11 and the second damper 12 according to the indoor air contamination status, the outside air temperature, the indoor air temperature, and the like. After suppressing the fluctuation|variation of the blowing temperature of the refrigerating-cycle apparatus 100 by this, an appropriate amount of ventilation can be performed.

In addition, when the refrigeration cycle device 100 does not perform ventilation, indoor air can flow to the second indoor heat exchange section 5 by operating the first damper 11 and the second damper 12 . In this case, the state of the air inside the indoor unit 3, that is, the heat exchange mechanism between the air and the refrigerant is the same as the heat exchange mechanism between the air and the refrigerant in the indoor unit of the conventional refrigeration cycle apparatus. Therefore, even if ventilation is not required, the refrigeration cycle device 100 can achieve efficiency similar to that of conventional refrigeration cycle devices.

The configuration of the refrigeration cycle device 100 described above is an example of the configuration of the refrigeration cycle device 100 in the present disclosure, and can be variously modified within the scope of the present disclosure.

FIG. 4 is a diagram showing another configuration example of the indoor unit 3. FIG. In FIG. 4, the second indoor fan 16 is provided, and the amount of indoor air flowing into the first indoor heat exchange section 4 and the amount of outdoor air flowing into the second indoor heat exchange section 5 are controlled independently. can be adjusted by In addition, a filter 17 is attached to the second suction port 14 in FIG. Filter 17 removes dust contained in the outside air. This makes it possible to supply cleaner outside air to the room.

Example 1.
An embodiment of the structure and operation of the indoor unit 3 will be described below. In addition, the flow of air inside the indoor unit 3 will also be described.

FIGS. 5(a) to 5(e) are diagrams showing the structure and operation of the indoor unit 3 of the refrigeration cycle apparatus 100 in Embodiment 1, and the flow of air inside the indoor unit 3. FIG. 5(a) is a perspective view showing the overall structure of the indoor unit 3a, FIG. 5(b) is a front view of the indoor unit 3a as seen from the front, and FIG. 5(c) is a rear view of the indoor unit 3a as seen from the rear. 5(d) and 5(e) are left views of the indoor unit 3a viewed from the left.

In the indoor unit 3a shown in FIGS. 5(a) to 5(e), a first suction port 13 for sucking indoor air is provided on the upper surface of the indoor unit 3a, and a second suction port 14a for sucking outside air is provided on the rear surface. there is A blowout port 15 provided with a wind direction adjusting means for adjusting the wind direction of the airflow blown out from the indoor unit 3a is provided at the lower front portion of the indoor unit 3a. Furthermore, the first indoor heat exchange units 4a and 4b, the second indoor heat exchange unit 5a, and the first indoor fan 6 are housed inside the indoor unit 3a.

Furthermore, a first damper 11a and a second damper 12a are accommodated inside the indoor unit 3a. The second damper 12a is arranged close to the second suction port 14a. The shape of the second damper 12a is substantially the same as the shape of the second suction port 14a, and the second damper 12a is slightly larger than the second suction port 14a. In the example shown in FIG. 5(c), the second damper 12a is arranged immediately below the second suction port 14a. Further, the second damper 12a is also rectangular, and the width and height of the second damper 12a are larger than the width and height of the second suction port 14a.

Further, the second damper 12a has an operation means (not shown), and has an open state that does not block the outside air flowing into the indoor unit 3a from the second suction port 14a, and an open state that blocks the second suction port 14a and prevents outside air from flowing into the indoor unit 3a. It operates to take a closed state that blocks inflow and a half-open state between the open and closed states. When the second damper 12a is in the closed state, the second damper 12a is larger than the second suction port 14a, so the second suction port 14a can be completely blocked.

Any type of operation means can be used for switching the state of the second damper 12a. For example, the second damper 12a may be operated by attaching a rotating shaft to one end of the second damper 12a and rotating the rotating shaft by power.

The first damper 11a is arranged inside the indoor unit 3a between the first suction port 13 and the second indoor heat exchange section 5a. In the example shown in FIGS. 5(a) and 5(d), the first damper 11a is attached below the first suction port 13 on the rear side of the indoor unit 3a.

The shape of the first damper 11a is not particularly limited. It is as large as it can be. For example, in the examples of FIGS. 5(a) and (d), the width of the first damper 11a is greater than the width of the first suction port 13, and the length of the first damper 11a is the rear surface of the indoor unit 3a. to the second indoor heat exchange section 5a. Since the first damper 11a has such a size, the indoor air is prevented from flowing into the second indoor heat exchange section 5a when the first damper 11a is in a closed state described later. be able to.

Further, the first damper 11a has an operation means (not shown), and is closed to prevent the indoor air sucked from the first suction port 13 from flowing into the second indoor heat exchange section 5a. It operates to take an open state that does not hinder the flow into the heat exchanging portion 5a and a half-open state between the open state and the closed state. When the first damper 11a is in the closed state, the width of the first damper 11a is longer than the width of the first suction port 13, and the length of the first damper 11a is two seconds from the rear surface of the indoor unit 3a. Since it is larger than the length up to the indoor heat exchange section 5a, it is possible to prevent the indoor air from flowing into the second indoor heat exchange section 5a.

Any means can be used as the operation means for switching the state of the first damper 11a regardless of its type. For example, the first damper 11a may be operated by attaching a rotating shaft to one end of the first damper 11a and rotating the rotating shaft by power.

FIGS. 5(d) and 5(e) show the airflow in the indoor unit 3a when the indoor unit 3a is viewed from the left. In FIG. 5(d), the second damper 12a is open and the first damper 11a is closed. On the other hand, in FIG. 5(e), the second damper 12a is closed and the first damper 11a is open.

In the state shown in FIG. 5(d), indoor air flows into the indoor unit 3a from the first suction port 13, and outside air flows from the second suction port 14a. The indoor air sucked from the first suction port 13 is blocked by the first damper 11a and does not flow into the second indoor heat exchange section 5a but flows into the first indoor heat exchange sections 4a and 4b. Also, since the second damper 12a is in the open state, outside air is sucked from the second suction port 14a and flows into the second indoor heat exchange section 5a.

At this time, if the refrigeration cycle apparatus 100 is operating in heating operation, the state of the first indoor heat exchange units 4a and 4b and the second indoor heat exchange unit 5a is supercooled as indicated by the solid line in FIG. The area is small and the efficiency of the whole heat exchanger is high.

On the other hand, in FIG. 5(e), the second damper 12a is closed and the first damper 11a is open. In the state shown in FIG. 5(e), while room air flows in from the first suction port 13, the second suction port 14a is blocked by the second damper 12a. Therefore, outside air does not enter. The indoor air that has flowed in from the first suction port 13 flows into the first indoor heat exchange sections 4a and 4b and the second indoor heat exchange section 5a.

At this time, if the refrigeration cycle device 100 is operating in the heating operation, the state of the first indoor heat exchange units 4a and 4b and the second indoor heat exchange unit 5a is such that outside air is not taken in as indicated by dotted lines in FIG. It is in the state of a conventional heat exchanger.

Example 2.
FIGS. 6(a) to 6(c) are diagrams showing the structure and operation of the indoor unit 3 and the flow of air inside the indoor unit 3 according to the second embodiment. Fig.6 (a) is a perspective view which shows the structure of the whole indoor unit 3b, FIG.6(b) and FIG.6(c) are the rear views which looked at the indoor unit 3b from the back. In addition, below, the difference between Example 1 shown in FIGS. 5A to 5E and Example 2 shown in FIGS. 6A to 6C will be described.

The indoor unit 3b shown in FIGS. 6(a) to 6(c) is provided with a second suction port 14b for sucking outside air on the rear surface. When compared with Example 1, Example 2 differs in the location and shape of the second suction port 14b. Further, the first indoor heat exchange units 4a, 4b, and 4c and the second indoor heat exchange units 5b and 5c are accommodated inside the indoor unit 3b. When compared with Example 1, Example 2 differs in the shapes of the first indoor heat exchange section 4 and the second indoor heat exchange section 5 .

Furthermore, a first damper 11b and a second damper 12b are accommodated inside the indoor unit 3b. The second damper 12b is arranged close to the second suction port 14b. The shape of the second damper 12b is substantially the same as the shape of the second suction port 14b, and the second damper 12b is larger than the second suction port 14b. In the example shown in FIG. 6(b), the second damper 12b is arranged on the right side of the second suction port 14b along the rear surface of the indoor unit 3b. Further, the second damper 12b is also substantially square with respect to the substantially square second suction port 14b, and the width and length of the second damper 12b are greater than the width and length of the second suction port 14b.

Furthermore, the second damper 12b has an operation means (not shown), and has an open state that does not block the outside air flowing into the indoor unit 3b from the second suction port 14b, and an open state that blocks the second suction port 14b and prevents outside air from flowing into the indoor unit 3b. It operates to take a closed state that blocks inflow and a half-open state between the open and closed states. In the example shown in FIG. 6(b), the second damper 12b is positioned on the right side of the second suction port 14b and is in an open state not blocking the second suction port 14b. On the other hand, in the example shown in FIG. 6(c), the second damper 12b has moved to a position where it blocks the second suction port 14b from the inside, and is in a closed state blocking the second suction port 14b. When the second damper 12b is in the closed state, the second damper 12b is larger than the second suction port 14b, so the second suction port 14b can be completely blocked.

Any type of operation means can be used as the operation means for switching the state of the second damper 12b. For example, a rail may be attached to the second damper 12b and the second damper 12b may be moved along the rail.

The first damper 11b is arranged inside the indoor unit 3b between the first suction port 13 and the second indoor heat exchange parts 5b and 5c. In the example shown in FIGS. 6(a) and 6(b), the first damper 11b is attached below the first suction port 13 and on the rear side of the indoor unit 3b.

Although the shape of the first damper 11b is not particularly limited, the size of the first damper 11b is such that the indoor air sucked from the first suction port 13 flows into the second indoor heat exchange portions 5b and 5c. It is large enough to prevent For example, in the example of FIGS. 6A and 6B, the width of the first damper 11b is greater than the width of the second indoor heat exchange section 5b, and the length of the first damper 11b is It is greater than the distance from the rear surface of the machine 3b to the front end of the second indoor heat exchange section 5b. Since the first damper 11b has such a size, it is possible to prevent indoor air from flowing into the second indoor heat exchange portions 5b and 5c when the first damper 11b is in a closed state described later. can be prevented.

Furthermore, the first damper 11b has an operation means (not shown), and has a closed state that prevents the indoor air sucked from the first suction port 13 from flowing into the second indoor heat exchange portions 5b and 5c. and a half-open state between the open state and the closed state. In the example shown in FIGS. 6(a) and 6(b), the first damper 11b is in the closed state. At this time, the width of the first damper 11b is larger than the width of the second indoor heat exchange section 5b, and the length of the first damper 11b is from the rear surface of the indoor unit 3b to the second indoor heat exchange section 5b. Greater than the distance to the front edge. Therefore, it is possible to prevent the indoor air from flowing into the second indoor heat exchange portions 5b and 5c. On the other hand, in the example shown in FIG. 6(c), the first damper 11b is in the open state. At this time, since the first damper 11b is not located between the first suction port 13 and the second indoor heat exchange portions 5b, 5c, the indoor air is not transferred to the second indoor heat exchange portions 5b, 5c. It does not impede inflow.

Any means can be used as the operation means for switching the state of the first damper 11b regardless of its type. For example, a rail may be attached to the first damper 11b and the first damper 12b may be moved along the rail.

Also, FIGS. 6(b) and 6(c) show the air flow inside the indoor unit 3b when the indoor unit 3b is viewed from behind. In FIG. 6B, the second damper 12b is open and the first damper 11b is closed. On the other hand, in FIG. 6(c), the second damper 12b is closed and the first damper 11b is open.

In the state shown in FIG. 6(b), indoor air flows into the indoor unit 3b from the first suction port 13, and outside air flows from the second suction port 14b. In addition, the indoor air sucked from the first suction port 13 is blocked by the first damper 11b and does not flow into the second indoor heat exchange units 5b and 5c, and the first indoor heat exchange units 4a, 4b, and Flow into 4c. Also, since the second damper 12b is in the open state, outside air is sucked from the second suction port 14b and flows into the second indoor heat exchange portions 5b and 5c.

At this time, if the refrigeration cycle apparatus 100 is operating in heating operation, the states of the first indoor heat exchange units 4a, 4b, 4c and the second indoor heat exchange units 5b, 5c are indicated by solid lines in FIG. Such a supercooling region is small and the efficiency of the entire heat exchanger is high.

On the other hand, in FIG. 6(c), the second damper 12b is closed and the first damper 11b is open. In the state shown in FIG. 6(c), while room air flows in from the first suction port 13, the second damper 12b blocks the second suction port 14b, so outside air flows from the second suction port 14b. does not flow. The indoor air that has flowed in from the first suction port 13 flows into the first indoor heat exchange sections 4a, 4b and 4c and the second indoor heat exchange sections 5b and 5c.

At this time, if the refrigeration cycle apparatus 100 is operating in heating operation, the states of the first indoor heat exchange units 4a, 4b, and 4c and the second indoor heat exchange units 5b and 5c are indicated by dotted lines in FIG. It is in the state of a conventional heat exchanger that does not take in the outside air as indicated by .

Example 3.
7(a) to 7(c) are diagrams showing the structure and operation of the indoor unit 3 and the flow of air inside the indoor unit 3 according to the third embodiment. FIG. 7(a) is a perspective view showing the overall structure of the indoor unit 3c, and FIGS. 7(b) and 7(c) are front views of the indoor unit 3c as seen from the front. 5(a) to 5(e), Example 2 shown in FIGS. 6(a) to 6(c), and FIGS. 7(a) to 7(c). The difference between the third embodiment shown in FIG.

In the indoor unit 3c shown in FIGS. 7(a) to 7(c), a second suction port 14c for sucking outside air is provided on the right side of the indoor unit 3c. When compared with the first and second embodiments, the third embodiment differs in the position where the second suction port 14c is provided. Further, inside the indoor unit 3c, similarly to the second embodiment, first indoor heat exchange units 4a, 4b, and 4c and second indoor heat exchange units 5b and 5c are accommodated.

Further, a first damper 11c and a second damper 12c are accommodated inside the indoor unit 3c. The second damper 12c is arranged close to the second suction port 14c. The shape of the second damper 12c is substantially the same as the shape of the second suction port 14c, and the second damper 12c is larger than the second suction port 14c. In the example shown in FIG. 7A, the second damper 12c is arranged below the second suction port 14c along the right surface of the indoor unit 3c. Further, the second damper 12c is also square with respect to the square second suction port 14c, and the width and length of the second damper 12c are larger than the width and length of the second suction port 14c.

Furthermore, the second damper 12c has an operation means (not shown), and has an open state that does not block the outside air flowing into the indoor unit 3c from the second suction port 14c, and an open state that blocks the second suction port 14c and prevents outside air from flowing into the indoor unit 3c. It operates to take a closed state that blocks inflow and a half-open state between the open and closed states. In the example shown in FIG. 7(b), the second damper 12c is positioned below the second suction port 14c and is in an open state not blocking the second suction port 14c. On the other hand, in the example shown in FIG. 7(c), the second damper 12c is in a closed state in which the second suction port 14c is blocked. When the second damper 12c is in the closed state, the second damper 12c is larger than the second suction port 14c, so the second suction port 14c can be completely blocked.

Any type of operation means can be used for switching the state of the second damper 12c. For example, the operating means of the second damper 12c may be manually operated by the user. FIGS. 8(a) and 8(b) are diagrams showing an example in which the operating means of the second damper 12c is manual. As shown in FIGS. 8(a) and 8(b), a notch 20 with a protrusion is provided on the right side of the indoor unit 3c, and a knob 21 movable along the notch 20 is attached to the second damper 12c, The user may move the knob 21 to operate the second damper 12c.

FIG. 8(a) is a view of the operating means when the second damper 12c is in an open state, and FIG. 8(b) is a view of the operating means when the second damper 12c is in a closed state. 8(a) and 8(b), a protrusion is also provided in the middle of the notch 20, but if the knob 21 is moved to the protrusion in the middle, the second damper 12c can be moved. It can be half open.

The first damper 11c is arranged inside the indoor unit 3c between the first suction port 13 and the second indoor heat exchange parts 5b and 5c. In the example shown in FIGS. 7(a) and 7(b), the first damper 11c is attached below the first suction port 13 on the rear side of the indoor unit 3c. The first damper 11c of this embodiment has substantially the same shape and operation as the first damper 11b of the second embodiment, but it is necessary not to interfere with the second damper 12c as described later. .

The shape of the first damper 11c is not particularly limited. It is large enough to prevent In the examples of FIGS. 7A and 7B, the width of the first damper 11c is larger than the width of the second indoor heat exchange section 5b, and the width of the first damper 11c is greater than that of the second indoor heat exchange section 5b, as in the second embodiment. The length is greater than the distance from the rear surface of the indoor unit 3c to the front end of the second indoor heat exchange section 5b.

In addition, the size of the first damper 11c is such that when the second damper 12c is in a closed state and the first damper 11c is in an open state, which will be described later, the first damper 11c is larger than the second damper 11c. It must be of a size that does not interfere with the damper 12c.

Furthermore, the first damper 11c has an operation means (not shown), and has a closed state that prevents the indoor air sucked from the first suction port 13 from flowing into the second indoor heat exchange portions 5b and 5c. and a half-open state between the open state and the closed state. In the example shown in FIGS. 7(a) and 7(b), the first damper 11c is closed. On the other hand, in the example shown in FIG. 7(c), the first damper 11c is in the open state.

Any type of operation means can be used for switching the state of the first damper 11c. The operation means of the first damper 11c is such that when the second damper 12c is in the closed state and the first damper 11c is in the open state, the first damper 11c moves to the second damper 12c. It must be of a size that does not interfere.

FIGS. 7(b) and 7(c) show the air flow inside the indoor unit 3c when the indoor unit 3c is viewed from the front. In FIG. 7B, the second damper 12c is open and the first damper 11c is closed. On the other hand, in FIG. 7C, the second damper 12c is closed and the first damper 11c is open.

In the state shown in FIG. 7(b), indoor air flows into the indoor unit 3c from the first suction port 13, and outside air flows from the second suction port 14c. In addition, the indoor air sucked from the first suction port 13 is blocked by the first damper 11c and does not flow into the second indoor heat exchange units 5b and 5c, and the first indoor heat exchange units 4a, 4b, and Flow into 4c. Also, since the second damper 12c is in the open state, outside air is sucked from the second suction port 14c and flows into the second indoor heat exchange portions 5b and 5c.

On the other hand, in FIG. 7(c), the second damper 12c is closed and the first damper 11c is open. In the state shown in FIG. 7(c), while room air flows in from the first suction port 13, the second damper 12c blocks the second suction port 14c, so outside air flows from the second suction port 14c. does not flow. The indoor air that has flowed in from the first suction port 13 flows into the first indoor heat exchange sections 4a, 4b and 4c and the second indoor heat exchange sections 5b and 5c.

At this time, if the refrigeration cycle apparatus 100 is operating in heating operation, the states of the first indoor heat exchange units 4a, 4b, and 4c and the second indoor heat exchange units 5b and 4c are indicated by dotted lines in FIG. It is in the state of a conventional heat exchanger that does not take in the outside air as indicated by .

As described above, the refrigeration cycle device 100 in the present disclosure has the first indoor heat exchange section 4 and the second indoor heat exchange section 5. Further, the indoor unit 3 is provided with a first suction port 13 for sucking indoor air and a second suction port 14 for sucking outside air. Furthermore, a first damper 11 and a second damper 12 are attached to the indoor unit 3 .

When the refrigerating cycle device 100 is performing heating operation, the second indoor heat exchange unit 5 is kept in a low temperature state by opening the second damper 12 and closing the first damper 11. Outside air can be introduced. As a result, ventilation is performed by taking outside air into the room. In addition, since the amount of heat exchanged between the refrigerant and the outside air increases in the indoor heat exchange section 5, the temperature of the outside air flowing into the indoor unit can be rapidly increased. Therefore, there is little possibility that the heating capacity will be lowered even though the room is ventilated by letting the outside air flow into the room.

Furthermore, the efficiency of the second indoor heat exchange section 5 is increased, and the high-to-low pressure ratio of the refrigerating cycle device 100 is reduced, so that energy saving of the refrigerating cycle device 100 is achieved. When the temperature of the outside air is about the same as the room temperature, or when the outside air is polluted, the second damper 12 is closed and the first damper 11 is opened. Operation similar to that of the cycle device can be performed.

In the first, second, and third embodiments, the first damper 11 and the second damper 12 are open or closed, but the first damper 11 and the second damper 12 are half-open. It can also be a state. Thereby, the amount of outside air and the amount of indoor air flowing into the second indoor heat exchange section 5 can be adjusted.

In addition, in

Embodiments

1, 2, and 3, a partition wall 18 can be provided in order to more reliably separate the indoor air flowing through the indoor unit 3 from the outside air.

9(a), (b), and (c) are diagrams showing the structure of the indoor unit 3a of Embodiment 1 when a partition wall 18 is provided inside the indoor unit 3a.

In the examples shown in FIGS. 9(a), (b), and (c), a partition wall 18 is attached to the rear surface of the indoor unit 3a, and the first damper 11a is arranged at the tip portion thereof. Therefore, in FIGS. 9(a), (b), and (c), both the partition wall 18 and the first damper 11a are arranged between the first suction port 13 and the second indoor heat exchange section 5a. be.

In addition, in the case shown in FIGS. 9(a), (b), and (c), the first damper 11a operates so as to rotate around the connection portion with the partition wall 18, for example. Specifically, in FIG. 9(b), the first damper 11a is in a closed state, and the first damper 11a prevents the indoor air sucked from the first suction port 13 from flowing to the second heat exchange section 5. impede On the other hand, in FIG. 9(c), the first damper 11a rotates around the connecting portion with the partition wall 18 and is in an open state. Therefore, the first damper 11 a does not prevent the indoor air sucked from the first suction port 13 from flowing into the second heat exchange section 5 .

By arranging the partition wall 18 and the first damper 11a in this way, it becomes easier to control the flow of air in the indoor unit 3a, and it becomes easier to exhibit the performance of the refrigeration cycle device as designed.

FIGS. 10(a) and 10(b) are diagrams showing the structure of the indoor unit 3b of Embodiment 2 when a partition wall 18 is provided inside the indoor unit 3b.

In FIGS. 10(a) and 10(b), a partition 18 is provided on the left side of the second suction port 14b. In FIG. 10(a), the second damper 12b is in an open state, and outside air is sucked into the indoor unit 3b from the second suction port 14 and flows to the second heat exchange section 5. In FIG. At this time, the indoor air is sucked into the indoor unit 3b from the first suction port 13, but the flow direction of this indoor air is limited by the first damper 11b and the partition wall 18, and the second heat exchange section The flow to 5 becomes extremely small.

Moreover, in FIG.10(b), the 1st damper 11b is an open state. Comparing FIG. 10(a) and FIG. 10(b), the first damper 11b moves left and right in the figure, but the partition wall 18 is provided so as not to hinder the movement of the first damper 11b. . Therefore, even if the partition wall 18 is provided, the function of the first damper 11b can be exhibited without any problem, and the flow of the indoor air and the outdoor air in the indoor unit 3b can be reliably controlled. It becomes easier to perform.

The refrigeration cycle apparatus of the present disclosure is particularly suitable for performing heating operation while ventilating.

1 compressor, 2 four-way valve, 3, 3, 3b, 3c indoor unit,
4, 4a, 4b, 4c first indoor heat exchange section,
5, 5a, 5b, 5c second indoor heat exchange section, 6 first indoor fan, 7 first air passage,
8 second air passage, 9 expansion valve, 10 outdoor heat exchanger,
11, 11a, 11b, 11c a first damper;
12, 12a, 12b, 12c second damper,
13 first suction port, 14, 14a, 14b, 14c second suction port,
15 outlet, 16 second indoor fan, 17 filter, 18 partition,
20 Notch 21 Knob 50 Control Device 100 Refrigerating Cycle Device

Claims

A refrigeration cycle device comprising an indoor unit,
The indoor unit is provided with a first suction port communicating with the room and a second suction port communicating with the outdoor,
a first heat exchange section arranged in a first air passage connecting the first inlet and the outlet;
The first heat exchanger is arranged in a second air passage connecting the second suction port and the outlet, and positioned downstream of the first heat exchange unit during heating operation of the refrigeration cycle device. a second heat exchange section connected to the section;
a first damper capable of adjusting the amount of air flowing from the first air passage to the second air passage;
a second damper provided at the second suction port and capable of adjusting the amount of air sucked from the second suction port;
refrigeration cycle device.
A partition wall separating the first air passage and the second air passage is provided inside the indoor unit,
The partition wall is provided with a communicating portion that communicates the first air passage and the second air passage,
The refrigeration cycle apparatus according to claim 1, wherein the first damper is attached to the communicating portion and is capable of adjusting the amount of air flowing through the communicating portion.
a first blower that sucks air from the first suction port and flows the air to the first heat exchange section; and a first blower that sucks outside air from the second suction port and flows the air to the second heat exchange section. The refrigeration cycle apparatus according to claim 1 or 2, comprising a second air blower.
The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein a dust collection filter is attached to the second suction port.
The refrigeration cycle apparatus according to any one of claims 1 to 4, wherein the second damper is larger than the second suction port.
The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the volume of the first heat exchange section is larger than the volume of the second heat exchange section.
The refrigeration cycle apparatus according to any one of claims 1 to 6, wherein the second suction port is provided on a rear surface of the indoor unit.
The refrigeration cycle apparatus according to any one of claims 1 to 6, wherein the second suction port is provided on a side surface of the indoor unit.