WO2022195834A1

WO2022195834A1 - Indoor unit and air conditioning device

Info

Publication number: WO2022195834A1
Application number: PCT/JP2021/011296
Authority: WO
Inventors: 惇司河野; 拓矢寺本; 裕樹宇賀神; 幸治山口; 哲央山下; 尚史池田
Original assignee: 三菱電機株式会社
Priority date: 2021-03-19
Filing date: 2021-03-19
Publication date: 2022-09-22
Also published as: EP4310404A4; CN117043517A; EP4310404A1; US20240077214A1; JPWO2022195834A1

Abstract

This indoor unit is provided with: a casing that has an air outlet and an air intake, with an airway being formed in the interior thereof; a cross flow fan that is disposed in the airway and blows out, from the air outlet, air that has been taken in from the air intake; a stabilizer for stabilizing a circulating vortex of air produced in the interior during rotation of the cross flow fan; and a guide wall constituting one surface of an outlet-side airway further downstream on the airway than the cross flow fan. The stabilizer has a first surface constituting one surface opposing the guide wall of the outlet-side airway. Part of the outlet-side airway is formed so that the distance from the first surface to the guide wall in the vertical direction gradually decreases going downstream.

Description

Indoor units and air conditioners

The present disclosure relates to indoor units and air conditioners equipped with cross-flow fans.

Conventionally, in an indoor unit of an air conditioner equipped with a cross-flow fan, there has been a problem that when air tends to flow back from the blower outlet, surging occurs, in which air is alternately blown out and sucked in from the blower outlet. . Therefore, an indoor unit with improved surging resistance has been proposed (see Patent Document 1, for example).

The indoor unit of Patent Document 1 includes a cross-flow fan arranged inside a casing, and a stabilizer that forms an air flow path between the cross-flow fan and an air outlet. A rough surface having unevenness is provided on the inclined surface of the protrusion on the downstream side in the blowing direction. The rough surface of the stabilizer makes it difficult for the blown air to separate from the stabilizer at the end of the blowout port, and by suppressing the backflow of air from the blowout port, surging resistance is improved.

JP 2018-124004 A

However, in the indoor unit of Patent Document 1, although the airflow along the stabilizer is difficult to separate, dust accumulates on the filter and the ventilation resistance increases. Since the airflow exceeds the protruding portion and the airflow along the stabilizer is reduced, the effect of suppressing the backflow from the outlet cannot be sufficiently obtained, and there is a problem that the surging resistance is reduced.

The present disclosure has been made to solve the above problems, and aims to provide an indoor unit and an air conditioner that suppress a decrease in surging resistance even when the operating load of the cross-flow fan is high. .

An indoor unit according to the present disclosure includes a casing having an air outlet and an air inlet and having an air passage formed therein; A fan, a stabilizer for stabilizing an air circulating vortex generated inside the cross-flow fan when the cross-flow fan rotates, and a guide wall forming one surface of the blow-out side air passage on the downstream side of the cross-flow fan in the air passage. and, the stabilizer has a first surface that constitutes one surface of the blowout-side air passage that faces the guide wall, and a part of the blowout-side air passage becomes the first The distance from the surface to the guide wall in the vertical direction is formed so as to gradually decrease.

Further, an air conditioner according to the present disclosure includes the indoor unit described above, and an outdoor unit that is connected to the indoor unit by pipes and constitutes a refrigerant circuit in which refrigerant circulates.

According to the indoor unit and the air conditioner according to the present disclosure, part of the outlet-side air passage is formed such that the distance from the first surface to the vertical guide wall gradually decreases toward the downstream. Therefore, it is possible to make the airflow uniform in the air passage on the blowing side. As a result, even when the operating load of the cross-flow fan is high due to the accumulation of dust on the filter and increased airflow resistance, it is difficult for a low-speed region to form in the air passage on the outlet side, causing the air to flow backwards from the outlet. Therefore, it is possible to suppress a decrease in surging resistance.

1 is a perspective view showing the appearance of an indoor unit according to Embodiment 1. FIG. 2 is a schematic vertical cross-sectional view of the indoor unit according to Embodiment 1. FIG. Fig. 2 is a schematic vertical cross-sectional view enlarging a main part of the indoor unit according to Embodiment 1; Fig. 10 is a schematic vertical cross-sectional view enlarging a main part of the indoor unit according to Embodiment 2; FIG. 11 is a first schematic vertical cross-sectional view enlarging a main part of an indoor unit according to Embodiment 3; FIG. 11 is a second schematic vertical cross-sectional view enlarging a main part of the indoor unit according to Embodiment 3; 7 is an arrow view of the ZZ section of FIG. 6. FIG. FIG. 11 is a schematic vertical cross-sectional view of an indoor unit according to Embodiment 4; FIG. 10 is a diagram showing a configuration example of an air conditioner according to Embodiment 5;

Hereinafter, embodiments of the present disclosure will be described based on the drawings. It should be noted that the present disclosure is not limited by the embodiments described below. Also, in the following drawings, the size relationship of each component may differ from the actual size.

Embodiment 1.
FIG. 1 is a perspective view showing the appearance of an indoor unit 100 according to Embodiment 1. FIG. FIG. 2 is a schematic vertical cross-sectional view of the indoor unit 100 according to Embodiment 1. FIG.

The configuration of the indoor unit 100 according to Embodiment 1 will be described below. In the following description, directional terms such as "up", "down", "right", "left", "front", and "back" are used as appropriate for ease of understanding. These terms are for the purpose of description and are not intended to be limiting of the embodiments. In addition, in the first embodiment, when the indoor unit 100 is viewed from the front (as viewed by the arrow X in FIG. 2), "upper", "lower", "right", "left", "front", and "rear" and so on.

The indoor unit 100 according to Embodiment 1 is a ceiling-embedded type installed in the ceiling. However, it is not limited to this, and the indoor unit 100 may be of a wall-mounted type, for example. As shown in FIGS. 1 and 2, the indoor unit 100 includes a box-shaped casing 1 embedded in the ceiling, a planar decorative panel 2 provided at the bottom of the casing 1 and serving as a design surface, and a decorative panel 2. and a flat plate-shaped intake grille 3 rotatably attached to it.

A suction port 1a for sucking indoor air is formed in the lower rear part of the casing 1, and an outlet 1b for blowing conditioned air to the outside is formed in the lower front part of the casing 1. The suction port 1a is covered with the suction grille 3 when the suction grille 3 is closed. In addition, the suction port 1a is provided with a filter 7 which is a porous member for removing dust, bacteria, and the like from the air. The room air sucked from the suction port 1 a passes through the filter 7 and is taken into the casing 1 . The outlet 1b is provided with a vertical vane 9a for changing the wind direction within a predetermined range in the vertical direction and a left and right vane 9b for changing the wind direction within a predetermined range in the horizontal direction.

Inside the casing 1, a cross-flow fan 6 that is rotatably arranged in the direction indicated by the arrow Y in FIG. It is arranged in a horizontal plane and inclined with respect to the depth direction, and heat exchange is performed between the indoor air sucked into the casing 1 from the suction port 1a by the cross flow fan 6 and the refrigerant to create conditioned air. A vessel 5 is provided. An air passage 20 is formed inside the casing 1 so that air flows from the inlet 1a through the heat exchanger 5 to the outlet 1b. It is located on the road 20.

The heat exchanger 5 is composed of an upper heat exchanger 5a and a lower heat exchanger 5b, and one end of the upper heat exchanger 5a and one end of the lower heat exchanger 5b are connected. The heat exchanger 5 is arranged such that the surface of the upper heat exchanger 5a facing the cross-flow fan 6 and the surface of the lower heat exchanger 5b facing the cross-flow fan 6 form an obtuse angle.

Furthermore, inside the casing 1, it is arranged below the heat exchanger 5 so as to face the entire lower heat exchanger 5b and the lower end of the upper heat exchanger 5a, and drain water from the heat exchanger 5 is drained. The drain pan 4 to be collected, the stabilizer 10 that divides the air passage 20 into the suction side air passage 20a on the upstream side of the cross flow fan 6 and the blowing side air passage 20b on the downstream side of the cross flow fan 6, and the blowing side wind A guide wall 11 forming one surface of the path 20b is provided.

Next, operation of the indoor unit 100 according to Embodiment 1 will be described.
As the motor rotates, the cross-flow fan 6 connected to the motor rotates, sucking the indoor air from the suction port 1a. Room air sucked from the suction port 1 a passes through the filter 7 and is sucked into the casing 1 . The indoor air drawn into the casing 1 passes through the heat exchanger 5 on the way through the suction-side air passage 20a, where it undergoes heat exchange and becomes conditioned air. After that, the conditioned air flows through the blow-out side air passage 20b and is blown into the room from the blow-out port 1b. At this time, the direction of the conditioned air blown from the outlet 1b changes depending on the directions of the upper and lower vanes 9a and the left and right vanes 9b.

FIG. 3 is a schematic vertical cross-sectional view showing an enlarged main part of the indoor unit 100 according to Embodiment 1. FIG.
Next, the details of the configuration of stabilizer 10 according to Embodiment 1 will be described.
The stabilizer 10 stabilizes the circulating vortex of air generated inside the cross-flow fan 6 when the cross-flow fan 6 rotates. This stabilizer 10, as shown in FIG. and a tongue 10c provided between 10a and the second surface 10b. Here, the tongue portion 10c is the vertex of the portion of the stabilizer 10 that protrudes toward the cross-flow fan 6 side. The second surface 10b is formed along the outer periphery of the crossflow fan 6, and a gap is formed between the second surface 10b and the crossflow fan 6. As shown in FIG. The gap between the second surface 10b and the crossflow fan 6 is the smallest at the position closest to the downstream side in the rotation direction of the crossflow fan 6 .

The first surface 10a has a contraction surface 10d formed so that the blow-out side air passage 20b contracts downstream from the tongue portion 10c. This contraction surface 10d is inclined so as to gradually approach the guide wall 11 as it goes downstream. Specifically, as indicated by the dashed arrow in FIG. 3, the contraction surface 10d is formed so that the distance from the surface to the guide wall 11 in the vertical direction gradually decreases toward the downstream. Further, if the position of the tongue portion 10c in the vertical direction is indicated by a dashed line H1, the position of the lower end of the outlet 1b by a dashed line H2, and the intermediate position thereof by a dashed line H3, the contraction surface 10d is located from the intermediate position (broken line H3). is also formed at a position on the upstream side. This is to make it easier to blow the conditioned air downward from the blowout port 1b. If the contraction surface 10d is formed at a position downstream of the intermediate position (broken line H3), it becomes difficult for the conditioned air to blow downward from the outlet 1b. As described above, part of the blow-out side air passage 20b is formed to contract downstream by the contraction surface 10d. Note that the contraction surface 10d may have a planar shape that is straight when viewed from the side as shown in FIG.

By providing the flow contraction surface 10d in the stabilizer 10 in this way, the airflow in the blow-out side air passage 20b can be made uniform, so that the airflow that does not follow the stabilizer 10 is reduced. As a result, even when the operating load of the cross-flow fan 6 increases due to the accumulation of dust on the filter 7 and the increase in airflow resistance, it becomes difficult for the blow-out side air passage 20b to create a low-velocity region. Since it becomes difficult for air to flow back from 1b, it is possible to suppress a decrease in surging resistance. In the blow-out side air passage 20b, the wind speed is low on the downstream side in the rotation direction of the cross flow fan 6, and the wind speed is high on the upstream side in the rotation direction of the cross flow fan 6, but the stabilizer 10 on the side where the wind speed is low A contraction surface 10d is formed on the first surface 10a of the . Therefore, it is possible to suppress an increase in pressure loss compared to forming a contracted flow surface having an inclination in the guide wall 11 on the high wind speed side.

As described above, the indoor unit 100 according to Embodiment 1 includes the casing 1 having the air outlet 1b and the air inlet 1a, and the air passage 20 formed therein, and the air passage 20 arranged in the air passage 20 to draw in air from the air inlet 1a. A cross-flow fan 6 that blows out air from the blow-out port 1b, a stabilizer 10 that stabilizes the circulation vortex of the air generated inside when the cross-flow fan 6 rotates, and an air passage 20 downstream of the cross-flow fan 6. and a guide wall 11 forming one surface of the blow-out side air passage 20b. The stabilizer 10 has a first surface 10a that constitutes one surface of the blowout-side air passage 20b facing the guide wall 11, and a part of the blowout-side air passage 20b extends downstream from the first surface 10a. It is formed so that the distance to the guide wall 11 in the vertical direction is gradually shortened.

According to the indoor unit 100 according to Embodiment 1, part of the outlet-side air passage 20b is formed such that the distance from the first surface 10a to the vertical guide wall 11 gradually decreases toward the downstream. Therefore, the airflow in the blow-out side air passage 20b can be made uniform. As a result, even when the operating load of the cross-flow fan 6 becomes high due to the accumulation of dust on the filter 7 and the increased ventilation resistance, a low air velocity region is less likely to occur in the outlet side air passage 20b. Since it becomes difficult for the air to flow back, it is possible to suppress a decrease in surging resistance.

In addition, in the indoor unit 100 according to Embodiment 1, the first surface 10a has a contraction surface 10d that is inclined so as to gradually approach the guide wall 11 toward the downstream side.

According to the indoor unit 100 according to Embodiment 1, the first surface 10a of the stabilizer 10 has the contraction surface 10d that is inclined so as to gradually approach the guide wall 11 as it goes downstream from the tongue portion 10c. That is, since the flow contraction surface 10d is formed on the first surface 10a of the stabilizer 10 on the low wind speed side, the flow contraction surface 10d is formed on the guide wall 11 on the high wind speed side rather than forming an inclined flow contraction surface. An increase in loss can be suppressed.

Embodiment 2.
Embodiment 2 will be described below, but descriptions of parts that overlap with those of Embodiment 1 will be omitted, and parts that are the same as or correspond to those of Embodiment 1 will be given the same reference numerals.

FIG. 4 is a schematic vertical cross-sectional view enlarging a main part of the indoor unit 100 according to Embodiment 2. As shown in FIG.
The first surface 10a of the stabilizer 10 has a downstream surface 10e on the downstream side of the contraction surface 10d, as shown in FIG. The angle between the plane connecting the upstream end and the downstream end of the downstream surface 10e and the vertical plane (dashed line V) is θ2, and the plane connecting the upstream end and the downstream end of the contraction surface 10d and the vertical plane (dashed line V) is defined as θ1, then θ2<θ1. In FIG. 4, θ2 is omitted because θ2=0°.

Thus, the angle between the plane connecting the upstream end and the downstream end of the downstream surface 10e and the vertical plane (broken line V) is the plane connecting the upstream end and the downstream end of the contraction surface 10d and the vertical plane ( By making the angle smaller than the angle with the dashed line V), the inclination of the blow-out side air passage 20b becomes gentle on the downstream side of the contraction surface 10d. As a result, the airflow in the blow-out side air passage 20b tends to be stabilized toward the blowout port 1b, and the airflow along the stabilizer 10 increases, so that surging resistance can be improved.

Also, the contraction surface 10d and the downstream surface 10e are formed so that the difference between θ2 and θ1 is 20° or less. This is because if the difference between θ2 and θ1 is too large, the airflow tends to separate on the stabilizer 10, and the airflow blown out from the cross-flow fan 6 tends to collide with the stabilizer 10 again after separation. This is because the pressure loss in the air passage 20b tends to increase. If the difference between .theta.2 and .theta.1 is 20.degree.

As described above, in the indoor unit 100 according to Embodiment 2, the first surface 10a has the downstream surface 10e on the downstream side of the contraction surface 10d, and is perpendicular to the plane connecting the upstream end and the downstream end of the downstream surface 10e. The angle formed with the surface (broken line V) is smaller than the angle formed between the plane connecting the upstream end and the downstream end of the contraction surface 10d and the vertical plane (broken line V).

According to the indoor unit 100 according to Embodiment 2, the angle between the plane connecting the upstream end and the downstream end of the downstream surface 10e and the vertical plane (broken line V) is the upstream end and the downstream end of the contraction surface 10d. and the vertical plane (broken line V). As a result, the airflow in the blow-out side air passage 20b tends to be stabilized toward the blowout port 1b, and the airflow along the stabilizer 10 increases, so that surging resistance can be improved.

Embodiment 3.
Embodiment 3 will be described below, but the description of the parts that overlap with

Embodiments

1 and 2 will be omitted, and the same or corresponding parts as those in

Embodiments

1 and 2 will be given the same reference numerals.

FIG. 5 is a first vertical cross-sectional schematic diagram enlarging the main part of the indoor unit 100 according to Embodiment 3. As shown in FIG. In FIG. 5, the position of the end of the crossflow fan 6 closest to the outlet in the horizontal direction is indicated by a broken line B, the position of the tongue portion 10c is indicated by a broken line A, and the position of the downstream end of the contraction surface 10d is indicated by a broken line C. showing.

In the third embodiment, as shown in FIG. 5, the end portion (dashed line B) of the cross flow fan 6 closest to the blowout port side in the horizontal direction is located horizontally between the tongue portion 10c (dashed line A) and the contraction surface 10d. , and the downstream end (dashed line C). By doing so, when the operating load of the cross-flow fan 6 is normal, the airflow blown out from the cross-flow fan 6 tends to lean toward the stabilizer 10 side. As a result, even when the operating load of the cross-flow fan 6 becomes high, the airflow blown out from the cross-flow fan 6 is less likely to shift to the guide wall 11 side, so that a low wind speed region is less likely to occur in the blow-out side air passage 20b. , it is difficult for the air to flow back from the outlet 1b.

When the tongue portion 10c (broken line A) is closer to the outlet 1b in the horizontal direction than the end (broken line B) closest to the outlet of the crossflow fan 6 in the horizontal direction, the tongue 10c is blown out from the crossflow fan 6. This makes it easier for the air current to flow toward the guide wall 11 side. As a result, when the operating load of the cross-flow fan 6 becomes high, the airflow blown out from the cross-flow fan 6 is more likely to move toward the guide wall 11, so that a low wind speed region is likely to be formed in the blow-out side air passage 20b. , air tends to flow back from the outlet 1b, resulting in a decrease in surging resistance. In addition, when the end of the crossflow fan 6 closest to the outlet in the horizontal direction (broken line B) is closer to the outlet 1b than the downstream end (broken line C) of the contraction surface 10d in the horizontal direction, the crossflow fan The airflow blown out from 6 is less likely to flow along the stabilizer 10 . As a result, the airflow blown out from the crossflow fan 6 separates from the stabilizer 10, becomes turbulent, and easily collides with each other. increase the driving load of

FIG. 6 is a second schematic vertical cross-sectional view enlarging the main part of the indoor unit 100 according to Embodiment 3. As shown in FIG. 7 is an arrow view of the ZZ section of FIG. 6. FIG.

Also, as shown in FIGS. 6 and 7, the distance from the downstream end of the flow contraction surface 10d to the guide wall 11 differs depending on the rotation axis direction of the cross flow fan 6 (hereinafter simply referred to as the rotation axis direction). Note that the direction of the rotation axis in FIG. 6 is the direction perpendicular to the plane of the paper. In the blow-out side air passage 20b, the distance from the downstream end of the contraction surface 10d to the guide wall 11 at both ends in the rotation axis direction is Lb1, and the distance from the downstream end of the contraction surface 10d at the center in the rotation axis direction is Assuming that the distance to the guide wall 11 is Lb2, Lb1<Lb2.

Here, due to the influence of both side surfaces (not shown) of the casing 1 forming both side surfaces of the blowout side air passage 20b, the speed of the air blown from the blowout port 1b is higher at both ends in the direction of the rotation axis. tend to be slower than the central part of the Low wind speed regions are likely to occur at both ends of the blowout side air passage 20b in the rotation axis direction, and air tends to flow backward from the blowout port 1b, so the surging resistance is likely to decrease. If the blow-out side air passage 20b is narrowed, the surging resistance can be improved because the airflow not along the stabilizer 10 is reduced. pressure loss increases.

Therefore, in the blow-out side air passage 20b, the distance from the downstream end of the flow contraction surface 10d at both ends in the rotation axis direction to the guide wall 11 is adjusted from the downstream end of the flow contraction surface 10d at the central portion in the rotation axis direction to the guide wall 11. Make it shorter than the distance to the wall 11. By doing so, while suppressing an increase in pressure loss at the central portion of the blowout-side air passage 20b in the rotation axis direction, airflow that does not follow the stabilizer 10 at both ends of the blowout-side air passage 20b in the rotation axis direction can be reduced. As a result, it is possible to suppress a decrease in surging resistance while suppressing an increase in pressure loss in the blow-out side air passage 20b.

As described above, in the indoor unit 100 according to Embodiment 3, the end of the crossflow fan 6 closest to the outlet 1b in the horizontal direction is located between the tongue 10c and the downstream end of the contraction surface 10d in the horizontal direction. positioned.

According to the indoor unit 100 according to Embodiment 3, by doing so, the airflow blown out from the cross-flow fan 6 tends to lean toward the stabilizer 10 when the operating load of the cross-flow fan 6 is normal. As a result, even when the operating load of the cross-flow fan 6 becomes high, the airflow blown out from the cross-flow fan 6 is less likely to shift to the guide wall 11 side, so that a low wind speed region is less likely to occur in the blow-out side air passage 20b. , it is difficult for the air to flow back from the outlet 1b.

Further, in the indoor unit 100 according to Embodiment 3, the distance from the downstream end of the contraction surface 10d to the guide wall 11 varies in the rotation axis direction of the cross flow fan 6, and the distance is the central portion in the rotation axis direction. The end portion in the rotation axis direction is shorter than the .

According to the indoor unit 100 according to Embodiment 3, in this way, while suppressing an increase in pressure loss at the central portion in the rotation axis direction of the blow-out side air passage 20b, the rotation of the blow-out side air passage 20b is suppressed. Airflow not along the stabilizer 10 at both ends in the axial direction can be reduced. As a result, it is possible to suppress a decrease in surging resistance while suppressing an increase in pressure loss in the blow-out side air passage 20b.

Embodiment 4.
Embodiment 4 will be described below, but descriptions of the same parts as those in Embodiments 1 to 3 will be omitted, and parts that are the same as or correspond to those in Embodiments 1 to 3 will be given the same reference numerals.

FIG. 8 is a schematic vertical cross-sectional view of the indoor unit 100 according to Embodiment 4. FIG. In FIG. 8, the position of the tongue portion 10c is indicated by a dashed line A, and the end of the heat exchanger 5 closest to the outlet in the horizontal direction is indicated by a dashed line D. As shown in FIG.
In the fourth embodiment, as shown in FIG. 8, the end portion (dashed line D) of the heat exchanger 5 closest to the blowout port side in the horizontal direction is positioned further toward the blowout port 1b than the tongue portion 10c (dashed line A) in the horizontal direction. located on the side. In addition, the end portion (dashed line D) of the heat exchanger 5 closest to the outlet in the horizontal direction may be positioned at the same position as the tongue portion 10c (dashed line A) in the horizontal direction. By doing so, the heat transfer area of the heat exchanger 5 can be increased, and the heat exchange efficiency can be improved. In addition, since the heat transfer area of the heat exchanger 5 is increased, the speed of the air passing through the heat exchanger 5 is reduced, thereby suppressing an increase in pressure loss in the air passage. Since likelihood is generated, it is possible to suppress a decrease in surging resistance.

As described above, the indoor unit 100 according to Embodiment 4 includes the heat exchanger 5 that exchanges heat between the air sucked from the suction port 1a by the cross flow fan 6 and the refrigerant. In the horizontal direction, the end closest to the outlet 1b is located at the same position as the tongue 10c or closer to the outlet 1b than the tongue 10c.

According to the indoor unit 100 according to Embodiment 4, by doing so, the heat transfer area of the heat exchanger 5 can be increased, and the heat exchange efficiency can be improved. In addition, since the heat transfer area of the heat exchanger 5 is increased, the speed of the air passing through the heat exchanger 5 is reduced, thereby suppressing an increase in pressure loss in the air passage. Since likelihood is generated, it is possible to suppress a decrease in surging resistance.

Embodiment 5.
Embodiment 5 will be described below, but the description of the parts overlapping those of Embodiments 1 to 4 will be omitted, and the same reference numerals will be given to parts that are the same as or correspond to those of Embodiments 1 to 4.

FIG. 9 is a diagram showing a configuration example of an air conditioner according to Embodiment 5. In FIG.

In the air conditioner shown in FIG. 9, an indoor unit 100 and an outdoor unit 200 are connected by gas refrigerant piping 300 and liquid refrigerant piping 400 to form a refrigerant circuit 500 in which refrigerant circulates. The indoor unit 100 is described in any one of the first to fourth embodiments. The outdoor unit 200 has a compressor 201 , a channel switching device 202 , an outdoor heat exchanger 203 , an outdoor fan 204 and an expansion device 205 .

The compressor 201 sucks in a low-temperature, low-pressure refrigerant, compresses the sucked-in refrigerant, and discharges a high-temperature, high-pressure refrigerant. The compressor 201 is, for example, an inverter compressor whose capacity, which is the output amount per unit time, is controlled by changing the operating frequency.

The flow path switching device 202 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the flow direction of the refrigerant. As the channel switching device 202, a combination of a two-way valve and a three-way valve may be used instead of the four-way valve.

The outdoor heat exchanger 203 exchanges heat between the outdoor air and the refrigerant. For example, during heating operation, it functions as an evaporator to evaporate and vaporize the refrigerant. Also, during cooling operation, it functions as a condenser to condense and liquefy the refrigerant.

The outdoor fan 204 is provided in the vicinity of the outdoor heat exchanger 203, and supplies outdoor air to the outdoor heat exchanger 203. By controlling the rotation speed, the air blowing amount to the outdoor fan 204 is adjusted. adjusted. As the outdoor fan 204, for example, a centrifugal fan or a multi-blade fan driven by a motor such as a DC (Direct Current) fan motor or an AC (Alternating Current) fan motor is used.

The expansion device 205 reduces the pressure of the refrigerant to expand it. The throttling device 205 is, for example, an electronic expansion valve that can adjust the opening of the throttling. Sometimes it controls the pressure of the refrigerant entering the outdoor heat exchanger 203 .

As described above, the air conditioner according to Embodiment 5 includes the indoor unit 100 described in any one of Embodiments 1 to 4, and the outdoor unit that constitutes a refrigerant circuit that is connected to the indoor unit 100 by piping and in which the refrigerant circulates. 200 and the like.

Since the air conditioner according to Embodiment 5 includes the indoor unit 100 according to any one of Embodiments 1 to 4, the indoor unit according to any one of Embodiments 1 to 4 is provided. An effect similar to that of 100 can be obtained.

1 Casing, 1a Suction port, 1b Air outlet, 2 Decorative panel, 3 Suction grille, 4 Drain pan, 5 Heat exchanger, 5a Upper heat exchanger, 5b Lower heat exchanger, 6 Cross flow fan, 7 Filter, 9a Upper and lower vanes , 9b left and right vanes, 10 stabilizer, 10a first surface, 10b second surface, 10c tongue, 10d contraction surface, 10e downstream surface, 11 guide wall, 20 air passage, 20a suction side air passage, 20b blowout side air passage , 100 Indoor unit, 200 Outdoor unit, 201 Compressor, 202 Flow switching device, 203 Outdoor heat exchanger, 204 Outdoor fan, 205 Expansion device, 300 Gas refrigerant pipe, 400 Liquid refrigerant pipe, 500 Refrigerant circuit.

Claims

a casing having an air outlet and an air inlet and having an air passage formed therein;
a cross-flow fan that is arranged in the air passage and blows out the air sucked from the suction port from the air outlet;
a stabilizer that stabilizes an air circulation vortex generated inside the cross flow fan when the cross flow fan rotates;
a guide wall forming one surface of the blowout side air passage downstream of the cross flow fan in the air passage,
The stabilizer is
having a first surface that constitutes one surface of the outlet-side air passage facing the guide wall;
A part of the blow-out side air passage is
The indoor unit is formed such that the distance from the first surface to the guide wall in the vertical direction gradually decreases toward the downstream side.
The first surface is
2. The indoor unit according to claim 1, comprising a contraction surface that is inclined so as to gradually approach the guide wall as it goes downstream.
The first surface has a downstream surface on the downstream side of the contraction surface,
The angle formed between the plane connecting the upstream end and the downstream end of the downstream surface and the vertical plane is smaller than the angle formed between the plane connecting the upstream end and the downstream end of the contraction surface and the vertical plane. Item 2. The indoor unit according to Item 2.
the distance from the downstream end of the contraction surface to the guide wall varies depending on the rotation axis direction of the cross flow fan,
The indoor unit according to claim 2 or 3, wherein the distance is shorter at the ends in the direction of the rotation axis than in the center part in the direction of the rotation axis.
The stabilizer is
The indoor unit according to any one of claims 2 to 4, further comprising a tongue portion which is a vertex of a portion projecting toward the cross flow fan.
The end of the crossflow fan closest to the outlet in the horizontal direction,
The indoor unit according to claim 5, wherein the tongue is positioned between the tongue and the downstream end of the contraction surface in the horizontal direction.
A heat exchanger that exchanges heat between the air sucked from the suction port by the cross-flow fan and the refrigerant,
The end of the heat exchanger closest to the outlet in the horizontal direction,
The indoor unit according to claim 5 or 6, wherein in the horizontal direction, it is located at the same position as the tongue or closer to the outlet side than the tongue.
The indoor unit according to any one of claims 1 to 7;
An air conditioner comprising: an outdoor unit that is connected to the indoor unit by pipes and forms a refrigerant circuit in which a refrigerant circulates.