Indoor unit and air conditioner

Abstract

One aspect of an indoor unit according to the present disclosure is an indoor unit for an air conditioner, the indoor unit comprising: a heat exchanger; a cross-flow fan; a housing that has a suction port and a blowout port and houses the heat exchanger and the cross-flow fan therein; and a stabilizer that separates the suction channel and the blowout channel of the cross-flow fan. The stabilizer has: a tongue portion that extends along the outer peripheral surface of the cross-flow fan and is provided with a facing surface that faces the cross-flow fan; a first protrusion that protrudes from the facing surface toward the cross-flow fan; and a second protrusion that protrudes from the facing surface toward the cross-flow fan and is located closer to the blowout channel than the first protrusion.

Description

Technical Field

[0001] The present disclosure relates to an indoor unit and an air conditioner.

Background Art

[0002] Conventionally, indoor units for air conditioners equipped with cross-flow fans are known. A stabilizer that separates a suction flow passage and a blowout flow passage of the cross-flow fan is provided inside such an indoor unit. The stabilizer forms a circulating vortex at a boundary between the suction flow passage and the blowout flow passage. This circulating vortex grows larger as the ventilation resistance at the suction port increases with the lapse of operating time of the indoor unit, and may draw indoor air with high humidity into the blowout port to cause dew condensation. Patent Document 1 discloses an indoor unit in which a protrusion is provided on the stabilizer to move the circulating vortex toward the suction flow passage side and suppress the occurrence of backflow.

Prior Art Literature

Patent Literature

[0003]

Patent Document 1

Summary of the Invention

Problem to be Solved by the Invention

[0004] In the indoor unit described in Patent Document 1, since the circulating vortex is moved toward the suction flow passage side by providing the protrusion, there is conversely a problem that the circulating vortex collides with the stabilizer when the ventilation resistance is low. When the stabilizer collides with the circulating vortex, pressure fluctuation at the collision portion increases, which causes a problem that the rotational noise of the cross-flow fan increases.

[0005] In view of the above circumstances, an object of the present disclosure is to provide an indoor unit capable of suppressing the occurrence of internal dew condensation and noise, and an air conditioner including such an indoor unit.

Means for Solving the Problem

[0006] One embodiment of an indoor unit according to the present disclosure is an indoor unit of an air conditioner, comprising: a heat exchanger; a cross-flow fan; a housing having an intake port and an outlet port and housing the heat exchanger and the cross-flow fan inside; and a stabilizer separating the intake passage and the discharge passage of the cross-flow fan, wherein the stabilizer has a tongue portion extending along the outer circumference of the cross-flow fan and having a facing surface facing the cross-flow fan; a first projection protruding from the facing surface toward the cross-flow fan; and a second projection protruding from the facing surface toward the cross-flow fan and positioned further toward the discharge passage than the first projection. The first projection has a first flow straightening surface that faces the discharge channel side and inclined toward the suction channel side as it approaches the tip, and the second projection has a second flow straightening surface that faces the discharge channel side and inclined toward the suction channel side as it approaches the tip, and the first and second flow straightening surfaces are each inclined toward the suction channel side at an acute angle with respect to the radial direction of the rotation axis. .

[0007] One embodiment of the air conditioner relating to this disclosure comprises the indoor unit and the outdoor unit described above. [Effects of the Invention]

[0008] According to this disclosure, it is possible to provide an indoor unit that can suppress the occurrence of internal condensation and noise, and an air conditioner equipped with such an indoor unit. [Brief explanation of the drawing]

[0009] [Figure 1] This is a schematic diagram showing the general configuration of an air conditioner in an embodiment. [Figure 2] This is a perspective view of the indoor unit in the embodiment. [Figure 3] This is a cross-sectional view of the indoor unit in the embodiment. [Figure 4] This is a perspective view of the stabilizer in the embodiment. [Figure 5] This is a magnified view of a portion of Figure 3. [Figure 6] This is a cross-sectional view of the indoor unit in an embodiment, schematically showing the first circulation vortex. [Figure 7] This is a cross-sectional view of the indoor unit in an embodiment, schematically showing the second circulation vortex. [Modes for carrying out the invention]

[0010] Embodiments of this disclosure will be described below with reference to the drawings. However, the scope of this disclosure is not limited to the embodiments described below and can be modified at will within the scope of the technical concept of this disclosure. Furthermore, in the following drawings, the scale and number of components in each structure may differ from those in the actual structure in order to make the configurations easier to understand.

[0011] Furthermore, the drawings show the X, Y, and Z axes as appropriate. The X axis represents one of the horizontal directions. The Y axis represents the other of the horizontal directions. The Z axis represents the vertical direction. In the following description, the horizontal direction along the X axis will be called the "front-back direction X," the horizontal direction along the Y axis will be called the "left-right direction Y," and the vertical direction will be called the "vertical direction Z." The front-back direction X, the left-right direction Y, and the vertical direction Z are all orthogonal to each other. In the following description, the side of the vertical direction Z in which the Z-axis arrow points (+Z side) will be considered the upper side, and the side of the vertical direction Z opposite to the side in which the Z-axis arrow points (-Z side) will be considered the lower side. Also, the side of the front-back direction X in which the X-axis arrow points (+X side) will be considered the front side, and the side of the front-back direction X opposite to the side in which the X-axis arrow points (-X side) will be considered the rear side. The left-right direction Y will be the left-right direction when the indoor unit of the following embodiment is viewed from the front (+X side). In other words, the right side is defined as the direction the Y-axis arrow points (+Y side) within the left-right Y direction, and the left side is defined as the opposite direction the Y-axis arrow points (-Y side).

[0012] Figure 1 is a schematic diagram showing the general configuration of the air conditioner 100 in this embodiment. As shown in Figure 1, the air conditioner 100 comprises an outdoor unit 10, an indoor unit 20, and a circulation path section 18. The outdoor unit 10 is located outdoors. The indoor unit 20 is located indoors. The outdoor unit 10 and the indoor unit 20 are connected to each other by a circulation path section 18 through which refrigerant 19 circulates.

[0013] The air conditioner 100 can adjust the temperature of the indoor air by exchanging heat between the refrigerant 19 flowing through the circulation path 18 and the air in the room where the indoor unit 20 is located. Examples of the refrigerant 19 include fluorine-based refrigerants or hydrocarbon-based refrigerants with a low global warming potential (GWP).

[0014] The outdoor unit 10 comprises a housing 11, a compressor 12, a heat exchanger 13, a flow control valve 14, a blower 15, a four-way valve 16, and a control unit 17. The compressor 12, heat exchanger 13, flow control valve 14, blower 15, four-way valve 16, and control unit 17 are housed inside the housing 11.

[0015] The compressor 12, heat exchanger 13, flow control valve 14, and four-way valve 16 are located in the part of the circulation path 18 that is inside the housing 11. The compressor 12, heat exchanger 13, flow control valve 14, and four-way valve 16 are connected by the part of the circulation path 18 that is located inside the housing 11.

[0016] The four-way valve 16 is installed in the part of the circulation path 18 that is connected to the discharge side of the compressor 12. The four-way valve 16 can reverse the direction of the refrigerant 19 flowing through the circulation path 18 by switching a part of the circulation path 18. If the path connected by the four-way valve 16 is the path shown by the solid line on the four-way valve 16 in Figure 1, the refrigerant 19 flows through the circulation path 18 in the direction shown by the solid arrow in Figure 1. On the other hand, if the path connected by the four-way valve 16 is the path shown by the dashed line on the four-way valve 16 in Figure 1, the refrigerant 19 flows through the circulation path 18 in the direction shown by the dashed arrow in Figure 1.

[0017] The indoor unit 20 includes a casing 21, a heat exchanger 22, a cross-flow fan 23 serving as a blower, and a control unit 24. The casing 21 houses the heat exchanger 22, the cross-flow fan 23, and the control unit 24 therein. The indoor unit 20 is capable of performing a cooling operation for cooling air in a room where the indoor unit 20 is installed, and a heating operation for heating air in the room where the indoor unit 20 is installed. Note that the cross-flow fan 23 is schematically illustrated in FIG. 1.

[0018] When the indoor unit 20 is operated in the cooling operation, the refrigerant 19 flowing in the circulation path portion 18 flows in the direction indicated by the solid-line arrow in FIG. 1. That is, when the indoor unit 20 is operated in the cooling operation, the refrigerant 19 flowing in the circulation path portion 18 circulates through the compressor 12, the heat exchanger 13 of the outdoor unit 10, the flow rate adjustment valve 14, and the heat exchanger 22 of the indoor unit 20 in this order to return to the compressor 12. In the cooling operation, the heat exchanger 13 in the outdoor unit 10 functions as a condenser, and the heat exchanger 22 in the indoor unit 20 functions as an evaporator.

[0019] On the other hand, when the indoor unit 20 is operated in the heating operation, the refrigerant 19 flowing in the circulation path portion 18 flows in the direction indicated by the broken line in FIG. 1. That is, when the indoor unit 20 is operated in the heating operation, the refrigerant 19 flowing in the circulation path portion 18 circulates through the compressor 12, the heat exchanger 22 of the indoor unit 20, the flow rate adjustment valve 14, and the heat exchanger 13 of the outdoor unit 10 in this order to return to the compressor 12. In the heating operation, the heat exchanger 13 in the outdoor unit 10 functions as an evaporator, and the heat exchanger 22 in the indoor unit 20 functions as a condenser.

[0020] Next, the indoor unit 20 will be described in more detail. FIG. 2 is a perspective view schematically showing the indoor unit 20. FIG. 3 is a cross-sectional view showing the indoor unit 20.

[0021] As shown in FIG. 2, the indoor unit 20 is a wall-mounted indoor unit fixed to an indoor wall surface WS. The indoor unit 20 has a substantially rectangular parallelepiped shape elongated in the left-right direction Y.

[0022] As shown in Figure 3, the cross-flow fan 23 is housed within the casing 21 of the indoor unit 20. The cross-flow fan 23 extends in the left-right direction Y. The cross-flow fan 23 rotates around a rotation axis R that extends in the left-right direction Y. The cross-flow fan 23 has a plurality of blades 23a arranged in the circumferential direction.

[0023] In the following explanation, unless otherwise specified, the direction parallel to the rotation axis R of the cross-flow fan 23 (the Y-axis direction) will simply be referred to as the "axial direction." The axial direction is the left-right direction Y of the indoor unit 20. The radial direction centered on the rotation axis R will simply be referred to as the "radial direction." The circumferential direction centered on the rotation axis R, that is, the direction around the axis of the rotation axis R, will simply be referred to as the "circumferential direction," and within the circumferential direction, the direction in which the cross-flow fan 23 rotates will be referred to as the rotational direction RD.

[0024] The heat exchanger 22 comprises a first heat exchanger 22a, a second heat exchanger 22b, and a third heat exchanger 22c. The first heat exchanger 22a is located in front of the cross-flow fan 23. The first heat exchanger 22a extends vertically in the Z direction when viewed in the left-right direction Y. The second heat exchanger 22b and the third heat exchanger 22c are located above the cross-flow fan 23. The second heat exchanger 22b extends upward and diagonally backward from the upper end of the first heat exchanger 22a when viewed in the left-right direction Y. The third heat exchanger 22c is located behind the second heat exchanger 22b. The third heat exchanger 22c extends downward and diagonally backward from the upper end of the second heat exchanger 22b when viewed in the left-right direction Y.

[0025] The housing 21 comprises an outer shell member 21b and an air passage member 21a. The outer shell member 21b is a component that forms part of the outer shell of the housing 21. The outer shell member 21b improves the aesthetic appearance of the indoor unit 20. The outer shell member 21b is a roughly rectangular box shape that opens to the rear. The rear opening of the outer shell member 21b is closed by the air passage member 21a.

[0026] The air passage member 21a is a component that forms part of the air passage through which the air drawn into the housing 21 by the cross-flow fan 23 passes. The air passage member 21a is hooked onto a mounting plate (not shown) which is fixed to the wall surface WS. This fixes the indoor unit 20 to the wall surface WS.

[0027] The air passage member 21a has a casing portion 29. The casing portion 29 extends along the outer circumference of the cross-flow fan 23 on the rear side of the cross-flow fan 23. The casing portion 29 gradually moves away from the outer circumference of the cross-flow fan 23 as it moves downward. The gap between the cross-flow fan 23 and the casing portion 29 on the underside of the cross-flow fan 23 forms the discharge passage F2 of the cross-flow fan 23. In this specification, "outer circumference of the cross-flow fan" means the cylindrical surface of the rotational trajectory of the radially outer end of the blade 23a provided on the cross-flow fan 23.

[0028] The housing 21 has an intake port 20a and an outlet port 20b. In this embodiment, the intake port 20a and the outlet port 20b are formed in the outer shell member 21b. The intake port 20a opens upward and extends in the axial direction. A filter 40 is placed in the intake port 20a. On the other hand, the outlet port 20b opens forward and downward and extends in the axial direction. A wind direction adjustment unit 25 is placed in the outlet port 20b. The wind direction adjustment unit 25 has left and right wind direction vanes 25a that adjust the wind direction in the left and right direction Y, and up and down wind direction vanes 25b that adjust the wind direction in the vertical direction Z.

[0029] Indoor air is drawn into the housing 21 through the intake port 20a by the drive of the cross-flow fan 23. The air drawn into the housing 21 through the intake port 20a passes through the filter 40 and then flows to the heat exchanger 22. The filter 40 captures at least some of the dust contained in the air passing through it. Furthermore, the air drawn into the housing 21 by the cross-flow fan 23 is blown out into the room through the outlet 20b. The air passing through the outlet 20b is blown in the vertical direction Z and the left-right direction Y of the room by the airflow direction adjustment unit 25.

[0030] The indoor unit 20 has a stabilizer 30. The stabilizer 30 is located inside the housing 21. The stabilizer 30 is located below the intake passage F1 and above the discharge passage F2. The stabilizer 30 separates the intake passage F1 and the discharge passage F2 of the cross-flow fan 23. The stabilizer 30 extends from the front panel of the housing 21 toward the underside of the cross-flow fan 23. The stabilizer 30 is located beneath the first heat exchanger 22a.

[0031] The stabilizer 30 has a top surface 35b located above the air outlet passage F2. In this embodiment, the top surface 35b faces downward. The top surface 35b is provided with left and right air direction vanes 25a and up and down air direction vanes 25b.

[0032] Figure 4 is a perspective view of the stabilizer 30. The stabilizer 30 is a resin molded product. The stabilizer 30 has a tongue portion 35, a first projection 31, a second projection 32, and a side plate portion 39. The tongue portion 35, the second projection 32, and the second projection 32 extend along the entire axial length of the cross-flow fan 23. That is, the tongue portion 35, the second projection 32, and the right end of the second projection 32 are located to the right (+Y side) of the right end of the cross-flow fan 23. The tongue portion 35, the second projection 32, and the left end of the second projection 32 are located to the left (-Y side) of the left end of the cross-flow fan 23.

[0033] As shown in Figure 3, the tongue portion 35 is positioned with a gap between it and the outer circumferential surface of the cross-flow fan 23. The tongue portion 35 has a tongue portion 35 that is positioned opposite the cross-flow fan 23. The tongue portion 35 extends along the outer circumferential surface of the cross-flow fan 23.

[0034] The tongue portion 35 is provided with an opposing surface 35a that faces the cross-flow fan 23. The opposing surface 35a faces radially inward. The opposing surface 35a has a uniform shape and extends axially.

[0035] The tongue portion 35 has an end portion 35c located on the side of the discharge channel F2. In the following description, the end portion of the tongue portion 35 on the side of the discharge channel F2 will simply be referred to as the end portion 35c. The end portion 35c has a curved surface that smoothly curves between the opposing surface 35a and the top surface 35b of the outlet 20b. As shown in Figure 4, the end portion 35c of the tongue portion 35 is provided with a plurality of slits 35s arranged in the axial direction.

[0036] Figure 5 is a magnified view of a portion of Figure 3. The first projection 31 protrudes from the opposing surface 35a of the tongue portion 35 toward the cross-flow fan 23. Similarly, the second projection 32 protrudes from the opposing surface 35a of the tongue portion 35 toward the cross-flow fan 23. The second projection 32 is located closer to the discharge flow path F2 than the first projection 31.

[0037] In this embodiment, the tongue portion 35 and the first projection portion 31 are both plate-shaped. That is, the first projection portion 31 is rib-shaped, extending from the tongue portion 35. Therefore, it is possible to suppress the localized increase in the thickness of the tongue portion 35 at the connection portion with the first projection portion 31. Consequently, when the tongue portion 35 is manufactured by mold molding, sink marks of the tongue portion 35 during molding can be suppressed, and as a result, the dimensional accuracy of each part of the stabilizer 30 can be improved.

[0038] Furthermore, in this embodiment, a recess 36 is provided between the first projection 31 and the tongue portion 35. The recess 36 is the space enclosed by the first projection 31 and the tongue portion 35. By forming the recess 36 between the first projection 31 and the tongue portion 35, the rigidity of the first projection 31 and the tongue portion 35 can be increased.

[0039] Furthermore, the recess 36 in this embodiment opens upward. Therefore, condensation water generated inside the housing 21 can be retained within the recess 36, and even if condensation water is generated inside the housing 21, it is possible to suppress the condensation water from dripping into the room from the outlet 20b. Moreover, the recess 36 in this embodiment is positioned directly below the front end (+X side end) of the cross-flow fan 23. Therefore, the recess 36 can efficiently receive condensation water dripping from the front end of the cross-flow fan 23.

[0040] In this embodiment, the second projection 32 is triangular in shape when viewed from the axial direction of the cross-flow fan 23. That is, the second projection 32 is composed of two surfaces: a flat second straightening surface (straightening surface) 32a facing the discharge passage F2 side, and a flat opposite surface 32b facing the suction passage F1 side. As will be described later, the second projection 32 has a lower protrusion height compared to the first projection 31. Therefore, by making the second projection 32 triangular in shape, it is easier to make the thickness of the tongue portion 35 uniform compared to the case where it is plate-shaped like the first projection 31. According to this embodiment, sink marks after molding of the second projection 32 can be suppressed, and the dimensional accuracy of each part of the stabilizer 30 can be improved.

[0041] Figures 6 and 7 are schematic diagrams showing the circulating vortices V1 and V2 formed inside the housing 21 by the cross-flow fan 23 and the stabilizer 30. Figure 6 shows the first circulating vortex V1 formed when the airflow resistance of the intake port 20a is high. On the other hand, Figure 7 shows the second circulating vortex V2 formed during steady-state conditions when sufficient airflow is secured in the intake passage F1.

[0042] In the following explanation, the state in which the first circulating vortex V1 shown in Figure 6 is formed will be referred to as the first state, and the state in which the second circulating vortex V2 shown in Figure 7 is formed will be referred to as the second state.

[0043] As shown in Figures 6 and 7, the circulating vortices V1 and V2 are swirling airflows that pass inside the cross-flow fan 23 and between the cross-flow fan 23 and the tongue portion 35. The circulating vortices V1 and V2 rotate clockwise when viewed from the right side (+Y side). In addition, the circulating vortices V1 and V2 are formed inside the housing 21, and a flow is formed that travels from the suction channel F1 across the inside of the cross-flow fan 23 to the discharge channel F2.

[0044] A discharge region A is provided between the circulating vortices V1 and V2 and the casing section 29. Discharge region A is an area that extends in the front-to-back direction and in the left-to-right direction Y of the discharge flow path F2. Of the air released from the cross-flow fan 23, the air that passes through discharge region A flows into the room from the outlet 20b. On the other hand, of the air released from the cross-flow fan 23, the air that passes in front of discharge region A (+X side) circulates inside and outside the cross-flow fan 23 as circulating vortices V1 and V2.

[0045] In the indoor unit 20 shown in Figure 3, dust continuously accumulates on the filter 40 as the operating time increases until the filter 40 is cleaned. In this case, the airflow resistance at the intake port 20a increases, and the pressure in the intake passage F1 decreases. The first state shown in Figure 6 appears when the pressure in the intake passage F1 decreases in this way. On the other hand, the second state appears when the airflow resistance at the intake port 20a is sufficiently low and the pressure in the intake passage F1 can be sufficiently maintained.

[0046] As shown in Figure 6, the first circulating vortex V1 in the first state is larger than the second circulating vortex V2, and the discharge area A narrows in the front-to-back direction. Furthermore, in the first state, the pressure in the intake passage F1 decreases, making it easier for indoor air to flow back into the housing 21 through the outlet 20b and be taken in by the first circulating vortex V1. When backflow occurs, the airflow efficiency deteriorates. Moreover, if backflow occurs during cooling operation, the high-humidity indoor air comes into contact with the low-temperature cross-flow fan 23, causing condensation to form on the blades 23a of the cross-flow fan 23.

[0047] According to this embodiment, a first projection 31 is provided on the opposing surface 35a of the tongue portion 35. The first projection 31 functions as the starting point 8a on the intake passage F1 side of the first circulating vortex V1, which has grown larger as the airflow resistance increases. That is, the air of the first circulating vortex V1 flows from the discharge passage F2 side to the suction passage F1 side along the opposing surface 35a of the tongue portion 35, hits the first projection 31, is swollen upwards, and enters the interior of the cross-flow fan 23. According to this embodiment, the position of the starting point 8a of the first circulating vortex V1 can be stabilized when the airflow resistance increases. This makes it possible to suppress the narrowing of the discharge region A on the (-X side) of the first circulating vortex V1, and to suppress the backflow of indoor air from the outlet 20b. As a result, not only can the airflow efficiency of the cross-flow fan 23 be increased, but condensation on the blades 23a of the cross-flow fan 23 can also be suppressed during cooling.

[0048] In this embodiment, the first projection 31 extends along the entire axial length of the cross-flow fan 23. Therefore, the starting point 8a of the first circulating vortex V1 can be the same regardless of the location in the axial direction. In other words, according to this embodiment, the first circulating vortex V1 of the same shape can be stably formed at any location in the axial direction.

[0049] As shown in Figure 7, in the second state where the pressure in the suction passage F1 is sufficiently high, the suction passage F1 is formed to be wide in the vertical direction Z. As a result, the second circulating vortex V2 becomes smaller than the first circulating vortex V1, and the discharge region A widens in the front-to-back direction. In this case, if only the first projection 31 is provided on the opposing surface 35a of the tongue portion 35, the circulating vortex collides head-on with the end portion 35c of the tongue portion 35, causing large pressure fluctuations. Such pressure fluctuations are the cause of the rotational noise of the cross-flow fan 23.

[0050] According to the present embodiment, in addition to the first protrusion 31, a second protrusion 32 is provided on the opposing surface 35a of the tongue portion 35. The second protrusion 32 is located closer to the blow-out flow path F2 side than the first protrusion 31. The second protrusion 32 functions as the starting point 8b of the second circulation vortex V2 on the suction flow path F1 side. That is, the air of the second circulation vortex V2 flows from the blow-out flow path F2 side toward the suction flow path F1 side along the opposing surface 35a of the tongue portion 35, hits the second protrusion 32, is rolled up upward, and enters the inside of the cross-flow fan 23. According to the present embodiment, the starting point 8b of the second circulation vortex V2 can be stabilized on the blow-out flow path F2 side relative to the first circulation vortex V1. This makes it easier for the air of the second circulation vortex V2 to flow along the opposing surface 35a of the tongue portion 35 without colliding against the end portion 35c of the tongue portion 35, thereby reducing pressure fluctuation in the vicinity of the end portion 35c of the tongue portion and reducing rotational noise of the cross-flow fan 23.

[0051] The second protrusion 32 of the present embodiment extends over the entire axial length of the cross-flow fan 23. Therefore, the starting point 8b of the second circulation vortex V2 can also be at the same position at any location in the axial direction. That is, according to the present embodiment, the second circulation vortex V2 having the same shape can be stably formed at any position in the axial direction.

[0052] As shown in FIG. 5, the first gap C1 between the first protrusion 31 and the cross-flow fan 23 is smaller than the second gap C2 between the second protrusion 32 and the cross-flow fan 23 (C1<C2). That is, the tip end of the first protrusion 31 is disposed closer to the cross-flow fan 23 than the tip end of the second protrusion 32. Note that the "distance between the protrusion and the cross-flow fan" means the "distance between the protrusion and the outer circumference of the cross-flow fan (that is, the rotation locus of the radially outer end of the blade)".

[0053] In the first state, the first circulating vortex V1 flows along the opposing surface 35a of the tongue portion 35, passes over the first projection 31, and then hits the second projection 32 and is swept upward. By making the second gap C2 larger than the first gap C1, the first circulating vortex V1 can be made to pass more easily between the first projection 31 and the cross-flow fan 23. Also, by making the first gap C1 smaller than the second gap C2, the first circulating vortex V1 can more easily hit the first projection 31, and the first projection 31 can function as the starting point 8a of the first circulating vortex V1. On the other hand, since the second circulating vortex V2 in the second state is a relatively small vortex, even if the second gap C2 is formed to be relatively wide, it is difficult for it to pass over the second projection 32, and it hits the second projection 32 and is swept upward.

[0054] As shown in Figure 5, in this embodiment, the difference between the first gap C1 and the second gap C2 (C2-C1) is preferably 0.5% or more of the diameter of the cross-flow fan 23. For example, if the outer diameter of the cross-flow fan 23 is 106 mm, the difference between the first gap C1 and the second gap C2 is preferably 0.6 mm or more. By having such a relationship between the first gap C1 and the second gap C2, the first circulating vortex V1 can be stably formed in the first state, and the second circulating vortex V2 can be stably formed in the second state.

[0055] In this embodiment, the first gap C1 is the narrowest gap between the stabilizer 30 and the cross-flow fan 23. The second gap C2 is the second narrowest gap between the stabilizer 30 and the cross-flow fan 23. In other words, the tongue portion 35, in parts other than the first projection 31 and the second projection 32, does not come any closer to the cross-flow fan 23 than the first projection 31 and the second projection 32. According to this embodiment, it is possible to suppress the functioning of the tongue portion 35, in parts other than the first projection 31 and the second projection 32, as an initiation point, making it easier to control the initiation point of the circulation vortex with the first projection 31 and the second projection 32.

[0056] As shown in Figure 5, when viewed from the axial direction of the cross-flow fan 23, the imaginary line connecting the rotation axis R of the cross-flow fan and the tip of the first projection 31 is defined as the first imaginary line L1. The imaginary line connecting the rotation axis R and the tip of the second projection 32 is defined as the second imaginary line L2. Furthermore, the imaginary line connecting the rotation axis R and the end portion 35c of the tongue portion 35 is defined as the third imaginary line L3.

[0057] According to this embodiment, the ratio of the angle α between the first virtual line L1 and the second virtual line L2 to the angle γ between the first virtual line L1 and the third virtual line L3 is greater than 50%. That is, the second projection 32 is located between the end portion 35c of the tongue portion 35 and the first projection 31, and is positioned biased toward the end portion 35c of the tongue portion 35.

[0058] If the second projection 32 is positioned biased toward the first projection 31, the second circulating vortex V2 is more likely to collide with the end 35c of the tongue portion 35 in the second state, and the effect of reducing pressure fluctuations near the end 35c of the tongue portion cannot be sufficiently obtained. According to this embodiment, by positioning the second projection 32 biased toward the end 35c of the tongue portion 35, the starting point 8b of the second circulating vortex V2 can be positioned sufficiently to the rear (-X side). This makes it easier for the air of the second circulating vortex V2 to flow along the opposing surface 35a of the tongue portion 35.

[0059] Furthermore, it is preferable that the ratio of the angle α between the first virtual line L1 and the second virtual line L2 to the angle γ between the first virtual line L1 and the third virtual line L3 is less than 62%. If the ratio of angle α to angle γ is too large, the second circulating vortex V2 formed in the second state will be too biased to the rear (-X side), causing the discharge region A to narrow in the front-to-back direction, reducing the airflow rate passing through the discharge channel F2, and potentially worsening the aerodynamic performance. According to this embodiment, by making the ratio of angle α to angle γ less than 62%, the width of the discharge region A can be sufficiently secured, and the airflow rate in the discharge channel F2 can be sufficiently secured.

[0060] The first projection 31 has a first straightening surface 31a facing the discharge passage F2 side. The first straightening surface 31a is inclined toward the suction passage F1 side as it approaches the tip side. Furthermore, the first straightening surface 31a of this embodiment has a first inclined portion 31e and a second inclined portion 31f, which have different inclination angles from each other. The first inclined portion 31e is located on the base side of the first projection 31, and the second inclined portion 31f is located on the tip side of the first projection 31. That is, the second inclined portion 31f is located on the tip side of the first projection 31 than the first inclined portion 31e.

[0061] The first inclination angle θ1 is defined as the inclination angle of the first inclined portion 31e with respect to a first virtual line (virtual line) L1 that extends radially from the rotation axis R of the cross-flow fan 23 toward the first inclined portion 31e. The second inclination angle θ2 is defined as the inclination angle of the second inclined portion 31f with respect to a first virtual line L1 that extends radially from the rotation axis R toward the second inclined portion 31f. The first inclination angle θ1 and the second inclination angle θ2 are the inclination angles of the first inclined portion 31e and the second inclined portion 31f with respect to the radial direction of the rotation axis R.

[0062] In this embodiment, the first inclination angle θ1 and the second inclination angle θ2 are both acute angles. Therefore, the first rectifying surface 31a of the first projection 31 is inclined toward the suction flow path F1 at an acute angle with respect to the radial direction over its entire length from the base to the tip.

[0063] If the first rectifying surface 31a is parallel to the radial direction of the rotation axis R, or inclined toward the discharge passage F2 side, the first circulating vortex V1 may collide with the first rectifying surface 31a, causing large pressure fluctuations and potentially increasing the rotation noise of the cross-flow fan 23. According to this embodiment, since the first rectifying surface 31a is inclined toward the suction passage F1 side at an acute angle with respect to the radial direction of the rotation axis R, the first circulating vortex V1 can be smoothly guided into the interior of the cross-flow fan 23 at the first projection 31.

[0064] In this embodiment, the second inclination angle θ2 is greater than the first inclination angle θ1. That is, the second inclined portion 31f has a greater inclination angle with respect to the radial direction of the cross-flow fan 23 than the first inclined portion 31e. Therefore, the first projection 31 rises steeply from the opposing surface 35a at the first inclined portion 31e, and then slopes gently toward the rotational direction of the cross-flow fan 23 at the second inclined portion 31f on the tip side.

[0065] As described above, the air of the first circulating vortex V1 passes between the opposing surface 35a of the tongue portion 35 and the outer circumference of the cross-flow fan 23. Also, the air of the first circulating vortex V1 hits the first projection 31 after passing over the second projection 32. After passing over the second projection 32, the air of the first circulating vortex V1 passes through a region that is biased towards the cross-flow fan 23 side than the tip of the second projection 32. Therefore, the air of the first circulating vortex V1 is more likely to hit the region of the first rectifying surface 31a of the first projection 31 that is closer to the cross-flow fan 23 (i.e., the second inclined portion 31f), and less likely to hit the first inclined portion 31e located at the base of the first projection 31.

[0066] According to this embodiment, by making the first inclined portion 31e a steep shape, the first projection 31 can be made smaller in the front-rear direction. Furthermore, according to this embodiment, since the first rectifying surface 31a has a bent shape at the tip, the rigidity of the first projection 31 can be increased compared to the case in which the entire first rectifying surface 31a is inclined at a uniform angle.

[0067] The second projection 32 has a second rectifying surface 32a facing the discharge passage F2 side. The second rectifying surface 32a is inclined toward the suction passage F1 side as it approaches the tip side. The inclination angle of the second rectifying surface 32a with respect to a second imaginary line (imaginary line) L2 that extends radially from the rotation axis R of the cross-flow fan 23 toward the second rectifying surface 32a is called the third inclination angle θ3. The first inclination angle θ1 and the second inclination angle θ2 are the inclination angles of the second rectifying surface 32a with respect to the radial direction of the rotation axis R. In this embodiment, the second rectifying surface 32a of the second projection 32 is inclined at an acute angle with respect to the radial direction of the rotation axis R throughout its entire length from the base side to the tip side.

[0068] If the second rectifying surface 32a is parallel to the radial direction of the rotation axis R, or inclined toward the discharge passage F2 side, the second circulating vortex V2 may collide with the second rectifying surface 32a, causing large pressure fluctuations and potentially increasing the rotation noise of the cross-flow fan 23. In this embodiment, since the second rectifying surface 32a is inclined toward the suction passage F1 side at an acute angle with respect to the radial direction of the rotation axis R, the first circulating vortex V1 can be smoothly guided into the interior of the cross-flow fan 23 at the second projection 32.

[0069] The configurations and methods described herein can be combined as appropriate, provided they are not mutually inconsistent.

[0070] For example, the above-described embodiment described a case where the intake port 20a is positioned on the upper side and the outlet port 20b is positioned on the lower side of the cross-flow fan 23. However, the arrangement of the intake port 20a and outlet port 20b with respect to the cross-flow fan 23 is not limited to this embodiment. [Explanation of Symbols]

[0071] 10...Outdoor unit, 21...Housing, 22...Heat exchanger, 20...Indoor unit, 20a...Intake port, 20b...Outlet port, 23...Cross-flow fan, 30...Stabilizer, 31...First projection, 31a...First straightening surface, 31e...First inclined section, 31f...Second inclined section, 32...Second projection, 32a...Second straightening surface (straightening surface), 32b...Opposite side, 35...Tongue, 35a...Opposite side, 35c...End, 36...Recess, 100...Air conditioner, C1...First gap, C2...Second gap, F1...Intake passage, F2...Outlet passage, L1...First virtual line (virtual line), L2...Second virtual line (virtual line), L3...Third virtual line (virtual line), L4...Virtual line, R...Rotation axis, α,γ...Angle

Claims

1. It is an indoor unit of an air conditioner, Heat exchanger, A cross-flow fan that rotates around the rotating axis, A housing having an intake port and an outlet port, which houses the heat exchanger and the cross-flow fan inside, The cross-flow fan comprises a stabilizer that separates the intake passage and the discharge passage, The aforementioned stabilizer is, A tongue portion extending along the outer circumferential surface of the cross-flow fan and having an opposing surface facing the cross-flow fan, A first projection that protrudes from the opposing surface toward the cross-flow fan, It has a second projection that protrudes from the opposing surface toward the cross-flow fan and is located toward the discharge passage side than the first projection, The first projection has a first flow straightening surface that faces the discharge channel side and is inclined toward the suction channel side as it approaches the tip side. The second projection has a second flow straightening surface that faces the discharge channel side and is inclined toward the suction channel side as it approaches the tip side. With respect to the radial direction of the rotating shaft, the first and second rectifying surfaces are inclined at an acute angle with respect to the radial direction of the rotating shaft toward the suction passage, over their entire length from the root to the tip. The first rectifying surface is, The first inclined section and It has a second inclined portion located closer to the tip of the first projection than the first inclined portion, The inclination angle of the second inclined portion with respect to the radial direction is greater than the inclination angle of the first inclined portion with respect to the radial direction. The inclination angle of the second rectifying surface with respect to the radial direction is smaller than the inclination angle of the second inclined portion with respect to the radial direction, and larger than the inclination angle of the first inclined portion with respect to the radial direction. Indoor unit.

2. The first gap between the first projection and the cross-flow fan is smaller than the second gap between the second projection and the cross-flow fan. The indoor unit according to claim 1.

3. The difference between the first gap and the second gap is 0.5% or more of the diameter of the cross-flow fan. The indoor unit according to claim 2.

4. Viewed from the axial direction of the aforementioned cross-flow fan, The imaginary line connecting the rotation axis and the tip of the first projection is defined as the first imaginary line. The imaginary line connecting the rotation axis and the tip of the second projection is defined as the second imaginary line. The imaginary line connecting the rotation axis and the end of the tongue portion on the blowing channel side is defined as the third imaginary line. The ratio of the angle between the first virtual line and the second virtual line to the angle between the first virtual line and the third virtual line is greater than 50%. An indoor unit according to any one of claims 1 to 3.

5. The tongue portion and the first projection portion are plate-shaped, The stabilizer has a recess that is surrounded by the tongue portion and the first projection portion and opens upward, An indoor unit according to any one of claims 1 to 4.

6. The second projection is composed of two surfaces: a flat, flow-straightening surface facing the discharge channel and a flat, opposite surface facing the suction channel. An indoor unit according to any one of claims 1 to 5.

7. The first projection and the second projection extend along the entire axial length of the cross-flow fan. An indoor unit according to any one of claims 1 to 6.

8. An indoor unit according to any one of claims 1 to 7, Outdoor unit and An air conditioner equipped with [a specific feature].

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