Indoor unit and air conditioner

Abstract

One aspect of an indoor unit according to the present disclosure is an indoor unit of an air conditioning system, comprising the indoor unit: a heat exchanger; a cross-flow fan; a housing comprising an intake opening and an exhaust opening, and containing the heat exchanger and the cross-flow fan; and a stabilizer; which separates an intake flow path and an exhaust flow path of the cross-flow blower, wherein the stabilizer comprises a tongue section extending along an outer circumferential surface of the cross-flow blower and having a facing surface which is directed towards the cross-flow blower, a first projection section which projects from the facing surface in the direction of the cross-flow blower, and a second projection section which projects from the facing surface in the direction of the cross-flow blower and which is arranged closer to the exhaust flow path than the first projection section.

Description

Technical area

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

[0002] An indoor air conditioner unit equipped with a cross-flow fan is known from the prior art. A stabilizer is provided inside such an indoor unit, separating an intake flow path and an exhaust flow path of the cross-flow fan. The stabilizer forms a circulating vortex at a boundary portion between the intake flow path and the exhaust flow path. The circulating vortex may become larger in a case where the ventilation resistance of an intake port increases as the operating time of the indoor unit increases, and may cause condensation by sucking humid indoor air into an exhaust port. Patent Document 1 discloses an indoor unit in which a protrusion is provided in a stabilizer to shift a circulating vortex closer to an intake flow path and suppress the occurrence of backflow. Citation listPatent document

[0003] Patent Document 1: Unexamined Japanese Patent Application Laid-Open No. 2004 - 150 789 Brief description of the inventionProblem to be solved by the invention

[0004] In the indoor unit described in Patent Document 1, since the circulating vortex is moved closer to the intake flow path by providing the protrusion, there is a problem that the circulating vortex collides with the stabilizer when the ventilation resistance is low. In a case where the stabilizer and the circulating vortex collide with each other, there is a problem that pressure fluctuation in a collision zone increases, and the rotation noise of the cross-flow fan becomes louder.

[0005] In view of the circumstances described above, it is an object of the present disclosure to provide an indoor unit configured to suppress the occurrence of internal condensation and the occurrence of noise, and to provide an air conditioner including the indoor unit. means of problem solving

[0006] One aspect of an indoor unit according to the present disclosure is an indoor unit of an air conditioner, the indoor unit comprising: a heat exchanger; a cross-flow fan; a casing including a suction port and a discharge port and accommodating therein the heat exchanger and the cross-flow fan;and a stabilizer separating an intake flow path and an exhaust flow path of the cross-flow fan from each other, the stabilizer comprising a tongue portion extending along an outer periphery of the cross-flow fan and having a facing surface facing the cross-flow fan, a first protrusion portion projecting from the facing surface toward the cross-flow fan, and a second protrusion portion projecting from the facing surface toward the cross-flow fan and disposed closer to the exhaust flow path than the first protrusion portion.

[0007] One aspect of an air conditioner according to the present disclosure includes: the indoor unit and an outdoor unit. Effects of the invention

[0008] According to the present disclosure, it is possible to provide an indoor unit capable of suppressing the occurrence of internal condensation and the occurrence of noise, and to provide an air conditioner including the indoor unit. Short description of the drawings Fig. 1 is a schematic diagram showing a schematic structure of an air conditioner according to an embodiment. Fig. 2 is a perspective view of an indoor unit according to the embodiment. Fig. 3 is a cross-sectional view of the indoor unit according to the embodiment. Fig. 4 is a perspective view of a stabilizer according to the embodiment. Fig. 5 is an enlarged fragmentary view showing a part of Fig. 3 shows. Fig. 6 is a cross-sectional view of the indoor unit according to the embodiment, and is a diagram schematically showing a first circulating vortex. Fig. 7 is a cross-sectional view of the indoor unit according to the embodiment, and is a diagram schematically showing a second circulating vortex. Description of embodiments

[0009] Hereinafter, an embodiment of the present disclosure will be described with reference to the drawings. The scope of the present disclosure is not limited to the following embodiment and can be modified in any way within the scope of the technical idea of ​​the present disclosure. In addition, in the following drawings, a scale and number of each structure may differ from a scale and number of an actual structure to facilitate understanding of each configuration.

[0010] Additionally, an X-axis, a Y-axis, and a Z-axis are shown in the drawings where appropriate. The X-axis indicates a direction in a horizontal direction. The Y-axis indicates another direction in the horizontal direction. The Z-axis indicates a vertical direction. In the following description, a horizontal direction along the X-axis is referred to as a "front-back direction X," a horizontal direction along the Y-axis is referred to as a "left-right direction Y," and a vertical direction is referred to as a "vertical direction Z." The front-back direction X, the left-right direction Y, and the vertical direction Z are mutually orthogonal directions.In the following description, a side (+Z side) in the vertical direction Z, in which an arrow on the Z-axis points, is defined as a top side, and a side (-Z side) in the vertical direction Z, which is opposite to the side in which the arrow on the Z-axis points, is defined as a bottom side. In addition, a side (+X side) in the front-back direction X, in which an arrow on the X-axis points, is defined as a front side, and a side (-X side) in the front-back direction X, which is opposite to the side in which the arrow on the X-axis points, is defined as a back side. In addition, the left-right direction Y is a left-right direction in a case where the indoor unit of the embodiment described below is viewed from the front (+X side).That is, a side (+Y-side) in the left-right direction Y, in which an arrow on the Y-axis points, is defined as a right side, and a side (-Y-side) in the left-right direction Y, which is opposite to the side in which the arrow on the Y-axis points, is defined as a left side.

[0011] Fig. 1 is a schematic diagram showing a schematic structure of an air conditioner 100 according to the present embodiment. As shown in Fig. As shown in Figure 1, the air conditioner 100 includes 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 via the circulation path section 18, through which a refrigerant 19 circulates.

[0012] The air conditioning system 100 enables heat exchange between the refrigerant 19 flowing inside the circulation path section 18 and the air in a room in which the indoor unit 20 is arranged, thereby regulating the temperature of the air in the room. Examples of the refrigerant 19 include a fluorine-based refrigerant with a low global warming potential (GWP) and a hydrocarbon-based refrigerant.

[0013] The outdoor unit 10 comprises a housing 11, a compressor 12, a heat exchanger 13, a flow control valve 14, a fan 15, a four-way valve 16 and a control unit 17. The compressor 12, the heat exchanger 13, the flow control valve 14, the fan 15, the four-way valve 16 and the control unit 17 are accommodated inside the housing 11.

[0014] The compressor 12, the heat exchanger 13, the flow control valve 14, and the four-way valve 16 are provided as parts of the circulation path section 18, which is arranged inside the housing 11. The compressor 12, the heat exchanger 13, the flow control valve 14, and the four-way valve 16 are connected by the parts of the circulation path section 18, which are arranged inside the housing 11.

[0015] The four-way valve 16 is provided in a part of the circulation path section 18 connected to a discharge side of the compressor 12. The four-way valve 16 can reverse a direction of the refrigerant 19 flowing inside the circulation path section 18 by switching between paths of parts of the circulation path section 18. In a case where the paths connected by the four-way valve 16, which are indicated by solid lines in the four-way valve 16 in Fig. 1, the refrigerant 19 flows inside the circulation path section 18 in a direction shown in Fig. 1 is indicated by a solid line arrow. Otherwise, in a case where the paths connected by the four-way valve 16 are the paths formed in the four-way valve 16 of Fig. 1 are indicated by dashed lines, the refrigerant 19 flows inside the circulation path section 18 in a direction which is Fig. 1 is indicated by an arrow with a dashed line.

[0016] The indoor unit 20 includes a housing 21, a heat exchanger 22, a cross-flow fan 23 as a fan, and a control unit 24. The housing 21 accommodates the heat exchanger 22, the cross-flow fan 23, and the control unit 24 within it. The indoor unit 20 can perform a cooling operation for cooling the air in the room in which the indoor unit 20 is arranged, and can perform a heating operation for heating the air in the room in which the indoor unit 20 is arranged. Fig. 1, the cross-flow fan 23 is shown schematically.

[0017] In a case where the indoor unit 20 performs the cooling operation, the refrigerant 19 flowing inside the circulation path portion 18 flows in the direction shown in Fig. 1 is indicated by a solid line arrow. That is, when the indoor unit 20 performs the cooling operation, the refrigerant 19 flowing inside the circulation path section 18 circulates to return to the compressor 12 after circulating through the compressor 12, the heat exchanger 13 of the outdoor unit 10, the flow control valve 14, and the heat exchanger 22 of the indoor unit 20 in this order. 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.

[0018] Otherwise, in a case where the indoor unit 20 performs the heating operation, the refrigerant 19 flowing inside the circulation path portion 18 flows in the direction shown in Fig. 1 is indicated by the dashed arrow. That is, when the indoor unit 20 performs the heating operation, the refrigerant 19 flowing inside the circulation path section 18 circulates to return to the compressor 12 after circulating through the compressor 12, the heat exchanger 22 of the indoor unit 20, the flow control valve 14, and the heat exchanger 13 of the outdoor unit 10 in this order. 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.

[0019] Next, the indoor unit 20 is 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.

[0020] As in Fig. As shown in Figure 2, the indoor unit 20 is a wall-mounted type indoor unit that is attached to a wall surface WS of the room. The indoor unit 20 has a substantially rectangular shape that is elongated in the left-right direction Y.

[0021] As in Fig. 3, the cross-flow fan 23 is housed in 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 about a rotation axis R extending in the left-right direction Y. The cross-flow fan 23 includes a plurality of blades 23a arranged in a circumferential direction.

[0022] In the following description, unless otherwise specified, a direction (Y-axis direction) parallel to the rotation axis R of the cross-flow fan 23 is simply referred to as an "axial direction." The axial direction is the left-right direction Y of the indoor unit 20. Further, a radial direction around the rotation axis R is simply referred to as a "radial direction." In addition, a circumferential direction around the rotation axis R, that is, a direction around the rotation axis R, is simply referred to as a "circumferential direction," and a direction in which the cross-flow fan 23 rotates in the circumferential direction is referred to as a rotation direction RD.

[0023] The heat exchanger 22 has a first heat exchanger 22a, a second heat exchanger 22b, and a third heat exchanger 22c. The first heat exchanger 22a is arranged in front of the cross-flow fan 23. The first heat exchanger 22a extends in the vertical direction Z as viewed from the left-right direction Y. The second heat exchanger 22b and the third heat exchanger 22c are arranged above the cross-flow fan 23. The second heat exchanger 22b extends upward and inclined backward in the left-right direction Y from an upper end portion of the first heat exchanger 22a. The third heat exchanger 22c is arranged behind the second heat exchanger 22b. As viewed in the left-right direction Y, the third heat exchanger 22c extends downward and inclined backward from an upper end portion of the second heat exchanger 22b.

[0024] The housing 21 has an outer shell element 21b and a wind path element 21a. The outer shell element 21b is a member that forms part of an outer shell of the housing 21. The outer shell element 21b improves the designability of an external appearance of the indoor unit 20. The outer shell element 21b has a substantially rectangular box shape that is open at the rear. An opening of the outer shell element 21b at the rear is blocked by the wind path element 21a.

[0025] The wind path element 21 is a member that forms part of a wind path through which the air drawn into the casing 21 by the cross-flow fan 23 passes. The wind path element 21a is suspended from a mounting plate (not shown) that is attached to the wall surface WS. Accordingly, the indoor unit 20 is attached to the wall surface WS.

[0026] The wind path member 21a includes a casing portion 29. The casing portion 29 extends along an outer periphery of the cross-flow fan 23 at a rear side of the cross-flow fan 23. The casing portion 29 is gradually spaced from the outer periphery of the cross-flow fan 23 toward a lower side of the casing portion 29. A blowout flow path F2 of the cross-flow fan 23 is formed in a gap between the cross-flow fan 23 and the casing portion 29 at a lower side of the cross-flow fan 23. In the present specification, the "outer periphery of the cross-flow fan" means a cylindrical surface of a rotation trajectory of a radially outer end portion of the blades 23a provided in the cross-flow fan 23.

[0027] The housing 21 has an intake port 20a and an exhaust port 20b. In the present embodiment, the intake port 20a and the exhaust 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 disposed in the intake port 20a. On the other hand, the exhaust port 20b opens forward and downward and extends in the axial direction. A wind direction adjusting portion 25 is disposed in the exhaust port 20b. The wind direction adjusting portion 25 has a left-right wind direction vane 25a that adjusts a wind direction in the left-right direction Y, and an up-down wind direction vane 25b that adjusts a wind direction in the vertical direction Z.

[0028] The air in the room is sucked into the interior of the casing 21 from the intake port 20a by driving the cross-flow fan 23. The air sucked into the casing 21 through the intake port 20a passes through the filter 40 and then flows to the heat exchanger 22. The filter 40 collects at least some of the dust contained in the air passing through the filter 40. Further, the air sucked into the casing 21 by the cross-flow fan 23 is blown out into the room through the exhaust port 20b. The air passing through the exhaust port 20b is blown into the room separately in the vertical direction Z and the left-right direction Y by the wind direction adjusting section 25.

[0029] The indoor unit 20 has a stabilizer 30. The stabilizer 30 is arranged inside the casing 21. The stabilizer 30 is arranged on a lower side of the intake flow path F1 and an upper side of the exhaust flow path F2. The stabilizer 30 separates the intake flow path F1 and the exhaust flow path F2 of the cross-flow fan 23 from each other. The stabilizer 30 extends from a panel on a front surface side of the casing 21 toward the lower side of the cross-flow fan 23. The stabilizer 30 is arranged on a lower side of the first heat exchanger 22a.

[0030] The stabilizer 30 includes an upper surface 35b located at the top of the exhaust flow path F2. The upper surface 35b of the present embodiment faces the bottom. The upper surface 35b is provided with the left-right wind direction blade 25a and the up-down wind direction blade 25b.

[0031] Fig. 4 is a perspective view of the stabilizer 30. The stabilizer 30 is a cast product. The stabilizer 30 has a tongue portion 35, a first protrusion portion 31, a second protrusion portion 32, and a side plate portion 39. The tongue portion 35, the second protrusion portion 32, and the second protrusion portion 32 extend over an entire axial length of the cross-flow fan 23. That is, right end portions of the tongue portion 35, the second protrusion portion 32, and the second protrusion portion 32 are located on the right side (+Y side) with respect to a right end portion of the cross-flow fan 23. Left end portions of the tongue portion 35, the second projection portion 32, and the second projection portion 32 are arranged on the left side (-Y side) with respect to a left end portion of the cross-flow fan 23.

[0032] As in Fig. As shown in Figure 3, the tongue portion 35 is arranged with a gap from an outer peripheral surface of the cross-flow fan 23. The tongue portion 35 has a facing surface 35a arranged to face the cross-flow fan 23. The tongue portion 35 extends along the outer peripheral surface of the cross-flow fan 23.

[0033] The tongue portion 35 is provided with the facing surface 35a, which faces the cross-flow fan 23. The facing surface 35a faces an inner side in the radial direction. The facing surface 35a extends in a uniform shape in the axial direction.

[0034] The tongue portion 35a has an end portion 35c located closer to a blow-out flow path F2. In the following description, the end portion of the tongue portion 35 located closer to the blow-out flow path F2 is simply referred to as an end portion 35c. The end portion 35c forms a curved surface that is seamlessly curved between the facing surface 35a and the upper surface 35b of the blow-out opening 20b. As shown in Fig. 4, a plurality of slots 35s arranged in the axial direction are provided in the end portion 35c of the tongue portion 35.

[0035] Fig. 5 is an enlarged partial view of Fig. 3. The first protrusion portion 31 protrudes from the facing surface 35a of the tongue portion 35 toward the cross-flow fan 23. Similarly, the second protrusion portion 32 protrudes from the facing surface 35a of the tongue portion 35 toward the cross-flow fan 23. The second protrusion portion 32 is located closer to the exhaust flow path F2 than the first protrusion portion 31.

[0036] According to the present embodiment, the tongue portion 35 and the first protrusion portion 31 are each plate-shaped. Specifically, the first protrusion portion 31 has a rib shape extending from the tongue portion 35. Therefore, it is possible to suppress a local increase in the thickness of the tongue portion 35 at a connecting portion with the first protrusion portion 31. Therefore, in a case where the tongue portion 35 is formed by casting, the generation of a sink mark in the tongue portion 35 during casting can be avoided, and as a result, the dimensional accuracy of each portion of the stabilizer 30 can be improved.

[0037] Additionally, in the present embodiment, a recessed portion 36 is provided between the first protrusion portion 31 and the tongue portion 35. The recessed portion 36 is a space surrounded by the first protrusion portion 31 and the tongue portion 35. By forming the recessed portion 36 between the first protrusion portion 31 and the tongue portion 35, the rigidity of the first protrusion portion 31 and the tongue portion 35 can be increased.

[0038] In addition, the recessed portion 36 according to the present embodiment opens toward the top. Therefore, condensation water generated in the casing 21 can be retained in the recessed portion 36, and even if the condensation water is generated in the casing 31, dripping of the condensation water into the space from the blowout port 20b can be prevented. Further, the recessed portion 36 of the present embodiment is disposed directly below a front end (end portion on the +X side) of the cross-flow fan 23. Therefore, the recessed portion 36 can efficiently retain the condensation water dripping from the front end of the cross-flow fan 23.

[0039] The second protrusion portion 32 of the present embodiment has a triangular shape when viewed in the axial direction of the cross-flow fan 23. That is, the second protrusion portion 32 is formed by two surfaces, specifically, a flat second rectifying surface (rectifying surface) 32a facing the discharge flow path F2 and a flat opposite side surface 32b facing the intake flow path F2. As described below, the second protrusion portion 32b has a smaller protrusion height than the first protrusion portion 31. By making the second protrusion portion 32 triangular, it is easier to uniform the thickness of the tongue portion 35 compared to a case where the second protrusion portion 32 has a plate shape like the first protrusion portion 31.According to the present embodiment, generation of a sink mark in the second protrusion portion 32 after molding can be avoided, and the dimensional accuracy for each portion of the stabilizer 30 can be increased.

[0040] The Fig. 6 and Fig. 7 are schematic diagrams showing circulating vortices V1 and V2 formed by the cross-flow fan 23 and the stabilizer 30 inside the casing 21. Fig. Fig. 6 is a diagram showing a first circulating vortex V1 formed in a case where a ventilation resistance of the intake port 20a is high. On the other hand, Fig. 7 is a diagram showing a second circulating vortex V2 formed during constant operation in which a sufficient air volume is ensured in the intake flow path F1.

[0041] In the following description, a condition in which the first circulating vortex V1, as shown in Fig. 6 is formed is referred to as a first state, and a state in which the second circulating vortex V2 as shown in Fig. 7 is referred to as a second state.

[0042] As in the Fig. 6 and Fig. As shown in Figure 7, the circulating vortices V1 and V2 are knot-like winds that pass through the interior of 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 from the right side (+Y side). Furthermore, the circulating vortices V1 and V2 are formed inside the casing 21, and a flow is formed from the intake flow path F1 through the interior of the cross-flow fan 23 to the exhaust flow path F2.

[0043] A blowout area A is provided between the circulating vortices V1 and V2 and the housing portion 29. The blowout area A is a region extending in the front-back direction and the left-right direction Y of the blowout flow path F2. The air flowing through the blowout area A among the air discharged from the cross-flow fan 23 flows into the interior of the room from the blowout port 20b. On the other hand, the air flowing through a front side (+X side) of the blowout area A among the air discharged from the cross-flow fan 23 circulates inside and outside the cross-flow fan 23 as the circulating vortices V1 and V2.

[0044] In the Fig. In the indoor unit 20 shown in Figure 3, dust continuously accumulates on the filter 40 with increasing operation time until it is cleaned. In this case, the ventilation resistance of the intake port 20a increases, and the pressure of the intake flow path F1 decreases. Fig. The first state shown in Figure 6 occurs in a case where the pressure of the intake flow path F1 decreases. On the other hand, the second state occurs in a case where the ventilation resistance of the intake port 20a is sufficiently low and the pressure of the intake flow path F1 can be sufficiently maintained.

[0045] As in Fig. 6, in the first state, the first circulating vortex V1 is larger than the second circulating vortex V2, and the blowout area A is reduced in the front-rear direction. Further, in the first state, since the pressure of the intake flow path F1 decreases, the air in the room flows back into the casing 21 via the blowout port 20b and is easily sucked into the first circulating vortex V1. In a case where backflow occurs, the blowing efficiency is deteriorated. Furthermore, in a case where backflow occurs during the cooling operation, humid indoor air comes into contact with the cross-flow fan 23 having a low temperature, and condensation occurs on the blades 23a of the cross-flow fan 23.

[0046] According to the present embodiment, the first protrusion portion 31 is provided on the facing surface 35a of the tongue portion 35. The first protrusion portion 31 functions as a starting point 8a of the first circulating vortex V1, which increases as the ventilation resistance increases on the intake flow path F1 side. That is, the air of the first circulating vortex V1 flows from the exhaust flow path F2 side along the facing surface 35a of the tongue portion 35 to the intake flow path F1 side, encounters the first protrusion portion 31, is blown to the upper side, and enters the interior of the cross-flow fan 23. In the present embodiment, a position of the starting point 8a of the first circulating vortex V1 can be stabilized in the case where the ventilation resistance increases.This can suppress the reduction of the blowout area A of the first circulating vortex V1 (-X side), thereby suppressing the backflow of the indoor air through the blowout port 2b. As a result, not only can the blowing efficiency of the cross-flow fan 23 be improved, but also the occurrence of condensation on the blades 23a of the cross-flow fan 23 during cooling operation can be prevented.

[0047] The first protrusion portion 31 of the present embodiment extends over the entire axial length of the cross-flow fan 23. Therefore, the starting point 8a of the first circulating vortex V1 can be set to the same position at any position in the axial direction. That is, according to the present embodiment, the first circulating vortex V1 having the same shape can be stably formed at any position in the axial direction.

[0048] As in Fig. As shown in Figure 7, in the second state where the pressure of the intake flow path F1 is sufficiently high, the intake flow path F1 is formed wide in the vertical direction Z. Therefore, the second circulating vortex V2 is smaller than the first circulating vortex V1, and the blowout area A is expanded in the front-rear direction. In this case, in a case where only the first protrusion portion 31 is provided on the facing surface 35a of the tongue portion 35, a circulating vortex collides head-on with the end portion 35c of the tongue portion 35 and causes a large pressure fluctuation. Such a pressure fluctuation causes rotation noise of the cross-flow fan 23.

[0049] According to the present embodiment, on the facing surface 35a of the tongue portion 35, in addition to the first protrusion portion 31, the second protrusion portion 32 is provided. The second protrusion portion 32 is located closer to the discharge flow path F2 than the first protrusion portion 31. The second protrusion portion 32 functions as a starting point 8b of the second circulating vortex V2 on the intake flow path F1 side. That is, the air of the second circulating vortex V2 flows from the discharge flow path F2 side along the facing surface 35a of the tongue portion 35 to the intake flow path F1 side, encounters the second protrusion portion 32, is blown upward to the upper side, and enters the interior of the cross-flow fan 23.According to the present embodiment, the starting point 8b of the second circulating vortex V2 on the exhaust flow path F2 side can be stabilized with respect to the first circulating vortex V1. Accordingly, the air of the second circulating vortex V2 is likely to flow along the facing surface 35a of the tongue portion 35 without colliding with the end portion 35c of the tongue portion 35, and the pressure fluctuation near the end portion 35c of the tongue portion is reduced, so that rotation noise of the cross-flow fan 23 can be reduced.

[0050] According to the present embodiment, the second protrusion portion 32 extends over the entire axial length of the cross-flow fan 23. Therefore, the starting point 8b of the second circulating vortex V2 can be at the same position at any location in the axial direction. That is, according to the present embodiment, the second circulating vortex V2, which has the same shape, can be stably formed at any position in the axial direction.

[0051] As in Fig. As shown in FIG. 5, a first gap C1 between the first protrusion portion 31 and the cross-flow fan 23 is smaller than a second gap C2 between the second protrusion portion 32 and the cross-flow fan 23 (C1 < C2). That is, a tip of the first protrusion portion 31 is located closer to the cross-flow fan 23 than a tip of the second protrusion portion 32. A "distance between the protrusion portion and the cross-flow fan" means a "distance between the protrusion portion and the outer periphery of the cross-flow fan (that is, the rotation trajectory of radially outer end portions of the blades)."

[0052] In the first state, the first circulating vortex V1 flows along the facing surface 35a of the tongue portion 35, impacts the second protrusion portion 32 after passing through the first protrusion portion 31, and is blown upward toward the top. By making the second gap C2 larger than the first gap C1, the first circulating vortex V1 can easily pass between the first protrusion portion 31 and the cross-flow fan 23. In addition, by making the first gap C1 smaller than the second gap C2, the first circulating vortex V1 can easily impact the first protrusion portion 31, and the first protrusion portion 31 can function as the starting point 8a for the first circulating vortex V1.On the other hand, since the second circulating vortex V2 is a relatively small vortex in the second state, even in a case where the second gap C2 is relatively large, it is difficult for the second circulating vortex V2 to cross the second protrusion portion 32, and the second circulating vortex V2 hits the second protrusion portion 32 and is blown up to the top.

[0053] As in Fig. 5, in the present embodiment, a difference (C2-C1) between the first gap C1 and the second gap C2 is preferably 0.5% or more of a diameter of the cross-flow fan 23. For example, in a case where an 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 setting the first gap C1 and the second gap C2 in such a relationship, 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.

[0054] In the present embodiment, the first gap C1 is the narrowest gap between the stabilizer 30 and the cross-flow fan 23. In addition, the second gap C2 is the second narrowest gap between the stabilizer 30 and the cross-flow fan 23. That is, portions of the tongue portion 35 except the first protrusion portion 31 and the second protrusion portion 32 are not closer to the cross-flow fan 23 than the first protrusion portion 31 and the second protrusion portion 32. According to the present embodiment, functions of the portions of the tongue portion 35 except the first protrusion portion 31 and the second protrusion portion 32 as a starting point can be suppressed, and the starting point of the circulating vortex can be easily controlled by the first protrusion portion 31 and the second protrusion portion 32.

[0055] As in Fig.5, an imaginary line connecting the rotational axis R of the cross-flow fan 23 and the tip of the first protrusion portion 31 is defined as a first imaginary line L1, as viewed in the axial direction of the cross-flow fan 23. In addition, an imaginary line connecting the rotational axis R and the tip of the second protrusion portion 32 is defined as a second imaginary line L2. Further, an imaginary line connecting the rotational axis R and the end portion 35c of the tongue portion 35 is defined as a third imaginary line L3.

[0056] According to the present embodiment, a ratio of an angle α between the first imaginary line L1 and the second imaginary line L2 to an angle γ between the first imaginary line L1 and the third imaginary line L3 is more than 50%. That is, the second protrusion portion 32 is biased between the end portion 35c of the tongue portion 35 and the first protrusion portion 31 toward one side of an end portion 35c of the tongue portion 35.

[0057] In a case where the second protrusion portion 32 is arranged to be biased toward the first protrusion portion 31, the second circulating vortex V2 in the second state is likely to collide with the end portion 35c of the tongue portion 35, and an effect of reducing the pressure fluctuation near the end portion 35c of the tongue portion 35 cannot be sufficiently achieved. According to the present embodiment, by arranging the second protrusion portion 32 to be biased toward the end portion 35c side of the tongue portion 35, the starting point 8b of the second circulating vortex V2 is sufficiently located at the rear side (-X side). Accordingly, the air of the second circulating vortex V2 can easily flow along the facing surface 35a of the tongue portion 35.

[0058] In addition, the ratio of the angle α between the first imaginary line L1 and the second imaginary line L2 to the angle γ between the first imaginary line L1 and the third imaginary line L3 is preferably less than 62%. In a case where the ratio of the angle α to the angle γ is too large, the second circulating vortex V2 formed in the second state is biased too much toward the rear (-X side), the blowout area A is narrowed in the front-rear direction, and the air volume passing through the blowout flow path F2 is reduced, which may deteriorate the aerodynamic performance. According to the present embodiment, a width of the blowout area A can be sufficiently secured, and the air volume of the blowout flow path F2 can also be sufficiently secured by setting the ratio of the angle α to the angle γ to less than 62%.

[0059] The first protrusion portion 31 has a first rectifying surface 31a facing the exhaust flow path F2. The first rectifying surface 31a is inclined toward the intake flow path F1 toward the tip side of the first protrusion portion 31. Further, the first rectifying surface 31a of the present embodiment has a first inclined portion 31e and a second inclined portion 31f having different inclination angles from each other. The first inclined portion 31e is located on a root side of the first protrusion portion 31, and the second inclined portion 31f is located on a tip side of the first protrusion portion 31. That is, the second inclined portion 31f is located closer to the tip side of the first protrusion portion 31 than the first inclined portion 31e.

[0060] The inclination angle of the first inclined portion 31e with respect to the first imaginary line (imaginary line) L1 extending from the rotational axis R of the cross-flow fan 23 to the first inclined portion 31e in the radial direction is referred to as a first inclination angle θ1. In addition, the inclination angle of the second inclined portion 31f with respect to the first imaginary line L1 extending in the radial direction from the rotational axis R to the second inclined portion 31f is referred to as a second inclination angle θ2. 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 rotational axis R.

[0061] In the present embodiment, the first inclination angle θ1 and the second inclination angle θ2 are each acute angles. Therefore, the first rectifying surface 31a of the first protrusion portion 31 is inclined at an acute angle with respect to the radial direction toward the intake flow path F1 over an entire range from the root side to the tip side.

[0062] In a case where the first rectifying surface 31a is inclined parallel to the radial direction of the rotation axis R or toward the exhaust flow path F2, there is a concern that the first circulating vortex V1 collides with the first rectifying surface 31a, causing a large pressure fluctuation and increasing the rotation noise of the cross-flow fan 23. According to the present embodiment, since the first rectifying surface 31a is inclined at an acute angle with respect to the radial direction of the rotation axis R toward the intake flow path F1, the first circulating vortex V1 can be smoothly guided to the interior of the cross-flow fan 23 at the first protrusion portion 31.

[0063] In the present embodiment, the second inclination angle θ2 is larger than the first inclination angle θ1. That is, the second inclined portion 31f has a larger inclination angle with respect to the radial direction of the cross-flow fan 23 than the first inclined portion 31e. Therefore, the first protrusion portion 31 rises steeply from the facing surface 35a in the first inclined portion 31e, and is gently inclined toward the rotation direction of the cross-flow fan 23 on the tip side in the second inclined portion 31f.

[0064] As described above, the air of the first circulating vortex V1 passes between the facing surface 35a of the tongue portion 35 and the outer periphery of the cross-flow fan 23. In addition, the air of the first circulating vortex V1 hits the first protrusion portion 31 after crossing the second protrusion portion 32. The air of the first circulating vortex V1 passes through a region biased toward the cross-flow fan 23 as the tip of the second protrusion portion 32 by crossing the second protrusion portion 32.Therefore, the air of the first circulating vortex V1 is more likely to hit a region of the first rectifying surface 31a of the first protruding portion 31 which is close to the cross-flow fan 23 (that is, the second inclined portion 31f), and is less likely to hit the first inclined portion 31e which is located on the root side of the first protruding portion 31.

[0065] In the present embodiment, by forming the first inclined portion 31e in a steep shape, the first protruding portion 31 can be reduced in the front-rear direction. In addition, according to the present embodiment, since the first rectifying surface 31a on the tip side has a curved shape, the rigidity of the first protruding portion 31 can be increased compared to a case where the entire first rectifying surface 31a is inclined at a uniform inclination angle.

[0066] The second protrusion portion 32 has the second rectifying surface 32a facing the discharge flow path F2. The second rectifying surface 32a is inclined toward a tip side of the second protrusion portion 32 toward the intake flow path F1. An inclination angle of the second rectifying surface 32a with respect to the second imaginary line (imaginary line) L2 extending in the radial direction from the rotational axis R of the cross-flow fan 23 toward the second rectifying surface 32a is referred to as a 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 rotational axis R.In the present embodiment, the second rectifying surface 32a of the second protruding portion 32 is inclined at an acute angle with respect to the radial direction of the rotation axis R over an entire range from the root side to the tip side.

[0067] In a case where the second rectifying surface 32 is parallel to the radial direction of the rotation axis R or inclined toward the exhaust flow path F2, there is a concern that the second circulating vortex V2 collides with the second rectifying surface 32a, causing a large pressure fluctuation and increasing the rotation noise of the cross-flow fan 23. According to the present embodiment, since the second rectifying surface 32a is inclined at an acute angle with respect to the radial direction of the rotation axis R toward the intake flow path F1, the first circulating vortex V1 can be smoothly guided to the interior of the cross-flow fan 23 at the second protrusion portion 32.

[0068] As described above, any configuration and method described in the present specification may be suitably combined within the scope of protection as long as they do not contradict each other.

[0069] For example, in the above-described embodiment, a case was described in which the intake port 20a is arranged at the top and the exhaust port 20b is arranged at the bottom with respect to the cross-flow fan 23. However, the arrangement of the intake port 20a and the exhaust port 20b with respect to the cross-flow fan 23 is not limited to this embodiment. [List of reference symbols] 10 outdoor unit 21 housings 22 heat exchangers 20 indoor unit 20a Intake opening 20b Exhaust opening 23 cross-flow blowers 30 Stabilizer 31 first projection section 31a first rectifying surface 31e first inclined section 31f second inclined section 32 second projection section 32a second rectifying surface (rectifying surface) 32b opposite side surface 35 tongue section 35a facing surface 35c final section 36 Return section 100 air conditioning C1 first gap C2 second slit F1 intake flow path F2 Blow-out flow path L1 first imaginary line (imaginary line) L2 second imaginary line (imaginary line) L3 third imaginary line (imaginary line) L4 imaginary line R axis of rotation α, γ angles QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] JP 2004 - 150 789

[0003]

Claims

[1] Indoor unit of an air conditioning system, comprising: a heat exchanger; a cross-flow fan rotating around a rotation axis; a housing comprising an intake opening and an exhaust opening, and accommodating the heat exchanger and the cross-flow fan in its interior; and a stabilizer which separates the intake flow path and an exhaust flow path of the cross-flow fan; wherein the stabilizer includes: a tongue portion extending along an outer peripheral surface of the cross-flow fan and having a facing surface facing the cross-flow fan, a first protrusion portion projecting from the facing surface toward the cross-flow fan, and a second protrusion portion protruding from the facing surface toward the cross-flow fan and disposed closer to the blow-out flow path than the first protrusion portion. [2] The indoor unit according to claim 1, wherein a first gap between the first protruding portion and the cross-flow fan is smaller than a second gap between the second protruding portion and the cross-flow fan. [3] The indoor unit according to claim 2, wherein a difference between the first gap and the second gap is 0.5% or more of a diameter of the cross-flow fan. [4] The indoor unit according to any one of claims 1 to 3, wherein, when viewed in the axial direction of the cross-flow fan, an imaginary line connecting the rotation axis and a tip of the first protruding portion is referred to as a first imaginary line, an imaginary line connecting the rotation axis and a tip of the second protruding portion is referred to as a second imaginary line, and an imaginary line connecting the rotation axis and an end portion of the tongue portion closer to the blow-out flow path is referred to as a third imaginary line, a ratio of an angle between the first imaginary line and the second imaginary line to an angle between the first imaginary line and the third imaginary line is greater than 50%. [5] Indoor unit according to one of claims 1 to 4, wherein the first protrusion portion has a first rectifying surface facing the exhaust flow path and inclined toward a side of the tip of the first protrusion portion toward the intake flow path, the second protrusion portion has a second rectifying surface facing the blow-out flow path and inclined toward a side of the tip of the second protrusion portion toward the intake flow path, and the first rectifying surface and the second rectifying surface are inclined with respect to a radial direction of the rotation axis at an acute angle of inclination in the direction of the intake flow path. [6] Indoor unit according to claim 5, wherein the first rectifying surface has a first inclined portion and a second inclined portion, which second inclined portion is arranged closer to the side of the tip of the first projection portion than the first inclined portion, and an inclination angle of the second inclined portion with respect to the radial direction is greater than an inclination angle of the first inclined portion with respect to the radial direction. [7] Indoor unit according to one of claims 1 to 6, wherein the tongue portion and the first projection portion are plate-shaped, and the stabilizer has a recessed portion surrounded by the tongue portion and the first projection portion 31 and opening upward. [8] The indoor unit according to any one of claims 1 to 7, wherein the second protruding portion is formed by a flat rectifying surface facing the blow-out flow path F2 and a flat opposite side surface facing the suction flow path. [9] The indoor unit according to any one of claims 1 to 8, wherein the first projection portion and the second projection portion extend over the entire axial length of the cross-flow fan. [10] Air conditioning system, comprising: the indoor unit according to one of claims 1 to 9; and an outdoor unit.

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