Air conditioner indoor unit

Abstract

To provide an indoor unit of an air conditioner with high heat exchange performance.SOLUTION: An indoor unit of an air conditioner 100 has a cabinet 1, a centrifugal fan 10, and an indoor heat exchanger 6. The centrifugal fan 10 has a motor 11, a plurality of vanes 12, a hub 13, and a shroud 14. The hub 13 has a bend 13b that is bent to the side of a top plate 1a more outside than the vanes 12 in the radial direction. The top plate 1a has a top plate slope 1av having an inclined slope that is inclined to increase in height position as it gets closer to the indoor heat exchanger 6 in the transverse direction. The top plate slope 1av is provided more inside than the indoor heat exchanger 6 in the radial direction of the rotation axis Z. In a longitudinal sectional view, an end of the bend 13b lies on the extension of the inclined slope.SELECTED DRAWING: Figure 4

Description

[Technical field]

[0001] The present invention relates to an indoor unit of an air conditioner. [Background technology]

[0002] As a technology for improving the airflow speed distribution of a heat exchanger in a ceiling-embedded indoor unit, for example, the technology described in Patent Document 1 is known. That is, Patent Document 1 describes bending the outer peripheral edge of the main plate of the centrifugal fan toward the upper end side of the heat exchanger. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 2-166323 Summary of the Invention [Problem to be solved by the invention]

[0004] In order to cool the motor, which is the driving source, a centrifugal fan is usually provided with a certain cooling hole near the rotating shaft of the main plate (also called a hub). In this case, a part of the high-pressure air discharged from the centrifugal fan flows toward the cooling hole through the gap between the top plate and the main plate, which causes a so-called leakage flow. The larger the flow rate of such leakage flow, the smaller the flow rate of air toward the upper part of the heat exchanger (near the top plate of the housing), and the lower the heat exchange performance. In the technology described in Patent Document 1, the leakage flow is not particularly taken into consideration, and the gap between the top plate and the main plate is relatively large, leaving room for improvement in the heat exchange performance of the indoor unit.

[0005] Therefore, an object of the present invention is to provide an indoor unit of an air conditioner having high heat exchange performance. [Means for solving the problem]

[0006] In order to solve the above-mentioned problems, an indoor unit of an air conditioner according to the present invention comprises a housing having a top plate and side plates, a centrifugal fan housed in the housing, and an indoor heat exchanger arranged within the housing to surround the centrifugal fan, the centrifugal fan comprises a motor as a drive source, a plurality of blades arranged at predetermined intervals in a circumferential direction, a hub installed on the top plate side of the plurality of blades and installed on a rotating shaft of the motor, and a shroud installed on the opposite side of the plurality of blades to the top plate, the hub has a curved portion that curves towards the top plate radially outward of the plurality of blades, the top plate has a top plate inclined portion including an inclined surface that is inclined so that a height position becomes higher the closer to the indoor heat exchanger in the lateral direction, and a thick portion provided over the entire inside area of ​​the top plate inclined portion, the thick portion is also provided directly above the motor, a surface of the thick portion facing the hub is flat, and a thickness of the thick portion in the vertical direction is constant in the radial direction and the circumferential direction of the rotating shaft of the motor and is equal to a difference in height from the upper end to the lower end of the inclined portion of the top plate; The vertical cross section of the portion including the top plate inclined portion and the thick portion has a trapezoidal shape with the inclined surfaces as a pair of legs, the top plate inclined portion is located radially inward of the indoor heat exchanger in the radial direction of the rotation shaft, and when viewed in vertical cross section, the end of the curved portion is located on an extension line of the inclined surface. Effect of the Invention

[0007] According to the present invention, it is possible to provide an indoor unit for an air conditioner having high heat exchange performance. [Brief description of the drawings]

[0008] [Figure 1] 1 is a configuration diagram of an air conditioner according to a first embodiment. [Diagram 2] FIG. 1 is a perspective view of an indoor unit of an air conditioner according to a first embodiment. [Diagram 3] 1 is a cross-sectional view of an indoor unit of an air conditioner according to a first embodiment, taken along a predetermined plane perpendicular to the rotation shaft of a centrifugal fan. [Figure 4] 2 is a vertical cross-sectional view of the indoor unit of the air conditioner according to the first embodiment taken along line II-II in FIG. [Diagram 5]5 is a partial enlarged view of an area C shown in FIG. 4 in the indoor unit of the air conditioner according to the first embodiment. [Figure 6] 13 shows simulation results for the flow speed of air passing through the indoor heat exchanger under the same air volume condition in the first embodiment and the comparative example. [Figure 7] FIG. 11 is a partially enlarged vertical cross-sectional view of an indoor unit of an air conditioner according to a second embodiment. [Figure 8] 3. FIG. 3 is a vertical cross-sectional view of an indoor unit of an air conditioner according to a third embodiment, taken along line III-III in FIG. [Figure 9] 13 is a simulation result showing the relationship between the value of ΔL / H and the volume of air passing through the indoor heat exchanger in the indoor unit of the air conditioner according to the fourth embodiment. [Figure 10] FIG. 4 is a vertical cross-sectional view of an indoor unit of an air conditioner according to a first modified example. [Figure 11] FIG. 11 is a vertical cross-sectional view of an indoor unit of an air conditioner according to a second modified example. [Figure 12] FIG. 4 is a vertical cross-sectional view of an indoor unit of an air conditioner according to a comparative example. [Figure 13] 13 is a partial enlarged view of an area C shown in FIG. 12 in an indoor unit of an air conditioner according to a comparative example. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] First Embodiment <Air conditioner configuration> FIG. 1 is a configuration diagram of an air conditioner W1 according to the first embodiment. In Fig. 1, the refrigerant piping Q1 is indicated by a solid line, and the communication line K1 is indicated by a dashed line. The air conditioner W1 is a device that performs air conditioning, and in the example of Fig. 1, it is equipped with four ceiling-embedded indoor units 100 and an upward-blowing outdoor unit 200. Although not shown, the outdoor unit 200 is equipped with a compressor, an outdoor heat exchanger, an outdoor fan, an expansion valve, etc. Each of the four indoor units 100 is equipped with an indoor heat exchanger 6 (see Fig. 4) and a centrifugal fan 10 (see Fig. 4).

[0010] In the refrigerant circuit in which the outdoor unit 200 and the four indoor units 100 are connected in a predetermined manner via refrigerant piping Q1, the refrigerant circulates in a refrigeration cycle. Note that in Fig. 1, the illustration of the refrigerant piping Q1 is simplified, and the gas side refrigerant piping and the liquid side refrigerant piping are indicated by a common solid line. Also, the outdoor unit 200 and the four indoor units 100 communicate in a predetermined manner via a communication line K1.

[0011] FIG. 2 is a perspective view of the indoor unit 100 of the air conditioner. As shown in Fig. 2, the indoor unit 100 includes a housing 1, a panel 2, a grill 3, and a louver 4. The housing 1 houses an indoor heat exchanger 6 (see Fig. 4) and a centrifugal fan 10 (see Fig. 4), which will be described later, and is box-shaped with an open bottom. When the indoor unit 100 is installed on the ceiling of an air-conditioned room, the housing 1 is disposed in the space above the ceiling.

[0012] The panel 2 is a plate-like member installed at the lower end of the housing 1, has a rectangular frame shape when viewed from below, and extends laterally outward beyond the housing 1. A long and narrow air outlet 5 is provided near each side of the panel 2 having a rectangular frame shape when viewed from below.

[0013] The grille 3 is a mesh member that guides air into the housing 1, and is installed at an opening in the rectangular frame-shaped panel 2. The air sucked into the housing 1 through the gaps in the grille 3 exchanges heat with the refrigerant flowing through the indoor heat exchanger 6 (see FIG. 4), and the air after heat exchange is blown out into the air-conditioned room through the air outlet 5.

[0014] The louvers 4 are plate-like members for adjusting the direction of air blown out through the air outlets 5, and one is provided for each of the four air outlets 5. The louvers 4 are rotated in a predetermined manner by a louver motor (not shown).

[0015] FIG. 3 is a cross-sectional view of the indoor unit 100 taken along a predetermined plane perpendicular to the rotation axis Z of the centrifugal fan 10. As shown in FIG. In addition to the components described above, the indoor unit 100 is equipped with a centrifugal fan 10 and an indoor heat exchanger 6 shown in Fig. 3. The centrifugal fan 10 is a blower that pressurizes air sucked in from below and blows the pressurized air toward the indoor heat exchanger 6. The centrifugal fan 10 is housed in the housing 1 and is installed near the center of the housing 1 when viewed in cross section.

[0016] The indoor heat exchanger 6 is a heat exchanger in which heat exchange takes place between the refrigerant flowing through its heat transfer tubes 6b (see FIG. 4) and the air blown out from the centrifugal fan 10, and is housed in the housing 1. As such an indoor heat exchanger 6, for example, a cross-fin tube type heat exchanger including a plurality of fins 6a (see FIG. 4) arranged at predetermined intervals and a plurality of heat transfer tubes 6b (see FIG. 4) penetrating these fins 6a is used.

[0017] The indoor heat exchanger 6 is bent in a predetermined manner and arranged so as to surround the centrifugal fan 10 inside the housing 1. Note that the indoor heat exchanger 6 being "arranged so as to surround the centrifugal fan 10" includes a case in which the indoor heat exchanger 6 completely surrounds the centrifugal fan 10 in cross-sectional view, as well as a case in which the indoor heat exchanger 6 surrounds most of the centrifugal fan 10 as shown in Fig. 3.

[0018] In the example of Fig. 3, the indoor heat exchanger 6 has a rectangular frame shape with rounded corners in a cross-sectional view (a cross-section taken along a predetermined plane perpendicular to the rotation axis Z of the centrifugal fan 10). More specifically, the indoor heat exchanger 6 is disposed so as to surround the centrifugal fan 10 with four straight sides (reference numbers not shown) and three rounded corners (reference numbers not shown). Note that a blocking member 20 is provided at a location where both ends of the indoor heat exchanger 6 are separated from each other to fill the space.

[0019] FIG. 4 is a vertical cross-sectional view of the air conditioner indoor unit 100 taken along line II-II in FIG. In addition to the above-mentioned components, the indoor unit 100 is equipped with a filter 7, a bell mouth 8, and a drain pan 9 shown in FIG. 4. The filter 7 collects dust from the air flowing into the housing 1 through the gap in the grill 3, and is installed above the grill 3. In the air flow direction, the grill 3, the filter 7, the bell mouth 8, and the centrifugal fan 10 are arranged in this order toward the downstream side. The housing 1 of the indoor unit 100 is equipped with a top plate 1a and a side plate 1b. The top plate 1a is a plate-like member that closes the upper opening of a cylinder (not shown) composed of the side plate 1b. The side plate 1b is a plate-like member that extends downward from the peripheral portion of the top plate 1a. A panel 2 (see also FIG. 2) is installed at the lower end of the side plate 1b.

[0020] The bellmouth 8 is a straightening member that guides the air drawn into the housing 1 through the grill 3 and the filter 7 in this order to the centrifugal fan 10. In cross section, the bellmouth 8 has a circular shape centered on the rotation axis Z of the centrifugal fan 10, and is installed below the centrifugal fan 10. The bellmouth 8 is curved in a predetermined manner so that the diameter of the circular shape decreases as it approaches the centrifugal fan 10 in the direction of the rotation axis Z. In the example of FIG. 4, the upper end of the bellmouth 8 is provided radially inside the lower end of the shroud 14.

[0021] The drain pan 9 receives condensation water that drips from the indoor heat exchanger 6 during cooling or dehumidifying operation, and is installed below the indoor heat exchanger 6. When a predetermined amount of condensation water accumulates in the drain pan 9, the condensation water is drained by operating a drain pump (not shown).

[0022] As described above, the centrifugal fan 10 has a function of pressurizing the air sucked from below and discharging the pressurized air toward the indoor heat exchanger 6. As shown in Fig. 4, the centrifugal fan 10 includes a motor 11, a plurality of blades 12, a hub 13, and a shroud 14.

[0023] The motor 11 is a drive source for the centrifugal fan 10, and includes a stator and a rotor, not shown. The rotating shaft of the motor 11 is mounted at the center of the hub 13. When the motor 11 is driven, the blades 12, the hub 13, and the shroud 14 rotate together. The motor 11 of the centrifugal fan 10 and the louver motor (not shown) are controlled in a predetermined manner by a control device (not shown).

[0024] The blades 12 are thin plate-like members that impart energy to the air by their movement, and are arranged at predetermined intervals in the circumferential direction. The upper edges of the blades 12 are attached to a hub 13, while the lower edges are attached to a shroud 14.

[0025] The hub 13 and the shroud 14 have the function of moving the blades 12 together with themselves as the motor 11 is driven, and also have the function of directing the air drawn in through the bellmouth 8 to the indoor heat exchanger 6. The hub 13 has a shape that is rotationally symmetrical with respect to the rotation axis Z of the motor 11. Specifically, the hub 13 has a circular shape in a cross section, and is curved in a predetermined manner in a vertical section (a section cut along a predetermined plane including the rotation axis Z of the motor 11) so that the diameter of the circular shape increases toward the top plate 1a. Note that a part of the hub 13 may extend laterally in a vertical section.

[0026] The hub 13 is installed on the top plate 1a side (i.e., the upper edge) of the multiple blades 12, and is also installed on the rotation axis Z of the motor 11. Since the hub 13 rotates as the motor 11 is driven, a predetermined gap is provided between the hub 13 and the top plate 1a so that the hub 13 does not come into contact with the top plate 1a. Meanwhile, the upper end of the indoor heat exchanger 6 comes into contact with the top plate 1a. Therefore, the height position of the hub 13 is lower than the upper end of the indoor heat exchanger 6. Note that a predetermined cooling hole (not shown) may be provided near the rotation axis Z of the hub 13 in order to cool the motor 11.

[0027] The shroud 14 has a predetermined shape that is rotationally symmetrical with respect to the rotation axis Z of the motor 11. The shroud 14 having such a configuration is installed on the opposite side of the top plate 1a of the plurality of blades 12 (i.e., on the lower edge). A circular opening provided at the lower end of the shroud 14 functions as an air intake port. The lengths H and ΔL shown in FIG. 4 will be described later.

[0028] FIG. 5 is a partial enlarged view of region C shown in FIG. In addition, although the indoor heat exchanger 6 is shown diagrammatically in Fig. 5, in reality, the lower end of the indoor heat exchanger 6 is located below the centrifugal fan 10 (see also Fig. 4). Moreover, the solid arrows in Fig. 5 indicate the flow of air. As shown in Fig. 5, the hub 13 includes a base portion 13a and a curved portion 13b. The base portion 13a is a portion on which the rotation axis Z (see Fig. 4) of the motor 11 and the plurality of blades 12 are mounted. In the example of Fig. 5, the periphery of the base portion 13a and the radially outer ends of the blades 12 are positioned substantially in the same radial position.

[0029] The curved portion 13b extends outward from the base portion 13a in a curved (upward) manner. That is, the curved portion 13b is curved toward the top plate 1a radially outward of the plurality of blades 12. Such curved portion 13b is provided over the entire area of ​​the hub 13 in the circumferential direction. Although details will be described later, by providing the hub 13 with the curved portion 13b, a portion of the air discharged from the centrifugal fan 10 is guided obliquely upward along the curved portion 13b.

[0030] An example of the shape of such curved portion 13b is a predetermined arc having a center of curvature at a predetermined position above hub 13 in a vertical cross-sectional view and contacting the edge of base portion 13a (the boundary with curved portion 13b). Note that, in Fig. 5, for ease of understanding, base portion 13a and curved portion 13b are illustrated as being distinct from each other, but base portion 13a and curved portion 13b are integral with each other.

[0031] The top plate 1a shown in FIG. 5 is formed of, for example, a heat insulating material. This suppresses heat exchange between the outside and inside of the housing 1, and thus suppresses condensation on the outer surface of the housing 1. In addition, the degree of freedom in designing when forming the top plate inclined portion 1av described below is increased, and the top plate 1a is also easily processed. As shown in FIG. 5, the top plate 1a includes a plate-shaped portion 1au, a top plate inclined portion 1av, and a thick portion 1aw. The plate-shaped portion 1au is a plate-shaped portion that closes the upper opening of the side plate 1b (see FIG. 3) that is cylindrical (octagonal in cross section). The edge of the plate-shaped portion 1au has a predetermined octagonal shape so as to correspond to the upper edge of the side plate 1b.

[0032] 5 has a function of directing air flowing obliquely upward along the curved portion 13b to the upper portion of the indoor heat exchanger 6, and is provided below the plate-shaped portion 1au. Moreover, in the radial direction of the rotation axis Z (see FIG. 4), the top plate inclined portion 1av is provided in an area inside the indoor heat exchanger 6 (inside the area surrounded by the indoor heat exchanger 6) and outside the hub 13.

[0033] The inclined top plate portion 1av includes an inclined surface G1 that is inclined so that the height position becomes higher as it approaches the indoor heat exchanger 6 in the horizontal direction. That is, the inclined surface G1 is formed so as to form a predetermined inclination angle θ1 with respect to a predetermined plane F1 (a plane including the lower surface of the plate-shaped portion 1au) perpendicular to the rotation axis Z (see FIG. 4). Also, as shown by the two-dot chain line in FIG. 5, in the vertical cross section, the end 131b of the curved portion 13b is provided on an extension line Ga1 of the inclined surface G1 of the inclined top plate portion 1av. With this configuration, the air that moves along the surface of the curved portion 13b is led directly to the upper part of the indoor heat exchanger 6 along the inclined surface G1 of the inclined top plate portion 1av by the so-called Coanda effect. As a result, the flow rate of the air passing through the upper part of the indoor heat exchanger 6 is increased, so that the heat exchange efficiency of the indoor heat exchanger 6 can be improved.

[0034] The "extension" of the inclined surface G1 is not limited to the "extension" in the strict sense. For example, the "extension" of the inclined surface G1 also includes the range of ±10° or less in the vertical cross section based on the extension Ga1 of the inclined surface G1. Both of the two boundaries (+10° boundary and -10° boundary: not shown) of the "range of ±10° or less" described above are assumed to be imaginary half-lines (not shown) with the end point being the point J1 where the inclined surface G1 and the plate-shaped portion 1au are in contact. Even within such an angle range, it is possible to suppress the air from peeling off or stagnating near the top plate inclined portion 1av.

[0035] It is also preferable that the surface of the curved portion 13b facing the indoor heat exchanger 6 and the inclined surface G1 (the surface facing the indoor heat exchanger 6) of the top plate inclined portion 1av are flush with each other. With this configuration, air moving along the surface of the curved portion 13b is easily guided to the inclined surface G1 of the top plate inclined portion 1av.

[0036] In addition, in a vertical cross-sectional view, it is preferable that the highest point J1 of the inclined surface G1 of the top plate inclined portion 1av is close to the indoor heat exchanger 6. Here, being "close" to the indoor heat exchanger 6 includes the case where the highest point J1 of the inclined surface G1 is in contact with the upper end of the indoor heat exchanger 6, as well as the case where it is near the upper end of the indoor heat exchanger 6 (for example, within a few centimeters). With this configuration, air that moves diagonally upward along the inclined surface G1 of the top plate inclined portion 1av is easily guided directly to the vicinity of the upper end of the indoor heat exchanger 6.

[0037] The top plate inclined portion 1av is provided over the entire circumferential direction of the rotation axis Z of the motor 11 so that the upper end of its inclined surface G1 (the portion J1 contacting the plate-shaped portion 1au) is aligned with the inner edge of the indoor heat exchanger 6 (see FIG. 3). In other words, when viewed from below, the top plate inclined portion 1av has a rectangular frame shape with four rounded corners to correspond to the shape of the indoor heat exchanger 6 (see FIG. 3). The indoor heat exchanger 6 (see FIG. 3) is provided on the outside of such a top plate inclined portion 1av.

[0038] The thick portion 1aw shown in Fig. 5 has a function of ensuring a predetermined thickness of the top plate 1a in the region inside the top plate inclined portion 1av. The thick portion 1aw is provided over the entire inner region of the top plate inclined portion 1av in the radial direction of the rotation axis Z of the motor 11 (see Fig. 4). In the example of Fig. 5, the thickness of the thick portion 1aw in the vertical direction is equal to the difference in height from the upper end to the lower end of the top plate inclined portion 1av. Note that the thickness of the thick portion 1aw in the vertical direction may be constant in the radial and circumferential directions of the rotation axis Z of the motor 11 (see Fig. 4).

[0039] In addition, in the radial direction of the rotation axis Z (see FIG. 4), it is preferable that the lower surface of the top plate 1a in the region inside the top plate inclined portion 1av (i.e., the lower surface of the thick portion 1aw) is lower in height than the lower surface of the top plate 1a in the region outside the top plate inclined portion 1av. This narrows the gap S between the top plate 1a (including the thick portion 1aw) and the hub 13 inside the top plate inclined portion 1av, so that the leakage flow P flowing into the gap S from the centrifugal fan 10 can be suppressed.

[0040] In addition, in Fig. 5, for ease of understanding, the plate-shaped portion 1au, the inclined top portion 1av, and the thick portion 1aw are illustrated as being distinguished from one another, but they may be integrally formed. The distance L1 and the vortex V shown in Fig. 5 will be described later.

[0041] <Actions and Effects> According to the first embodiment, as shown in Fig. 5, the hub 13 of the centrifugal fan 10 has a curved portion 13b, while the top plate 1a of the housing 1 has a top plate inclined portion 1av. In vertical cross section, an end 131b of the curved portion 13b is provided on an extension line Ga1 of the inclined surface G1 of the top plate inclined portion 1av. With this configuration, part of the air discharged from the centrifugal fan 10 flows obliquely upward along the curved portion 13b due to the Coanda effect, and is further guided directly to the upper part of the indoor heat exchanger 6 along the inclined surface G1 of the top plate inclined portion 1av.

[0042] Therefore, the flow rate of air passing through the upper part of the indoor heat exchanger 6 becomes relatively large, thereby improving the heat exchange efficiency of the indoor heat exchanger 6. The air flow in such an indoor unit 100 will be described in detail while comparing it with a comparative example (see Figs. 12 and 13) that does not have the curved portion 13b or the top plate inclined portion 1av.

[0043] FIG. 12 is a vertical cross-sectional view of an indoor unit 100F of an air conditioner according to a comparative example. 12 differs from the first embodiment in that the hub 13F of the centrifugal fan 10F does not include the curved portion 13b (see FIG. 5), and the top plate 1Fa does not include the top plate inclined portion 1av (see FIG. 5) or the thick portion 1aw (see FIG. 5). Note that the other configurations are the same as those of the first embodiment, and therefore will not be described.

[0044] FIG. 13 is a partial enlarged view of region C shown in FIG. The solid arrows in Fig. 13 indicate the flow of air. In the comparative example in Fig. 13, air discharged radially outward from the centrifugal fan 10F moves approximately perpendicular to the fins 6a (see Fig. 12) of the indoor heat exchanger 6. Here, as described above, the height position of the upper end of the indoor heat exchanger 6 is higher than the hub 13F, so the flow rate of air passing over the upper part of the indoor heat exchanger 6 is relatively small.

[0045] 13, the high-pressure air discharged from the centrifugal fan 10F pushes the air near the top of the indoor heat exchanger 6 radially inward through the gap S between the top plate 1Fa and the hub 13F. Because of this leakage flow P, the air near the top plate 1Fa does not flow toward the top of the indoor heat exchanger 6, but flows toward the rotation axis Z (see FIG. 12) of the centrifugal fan 10F.

[0046] Meanwhile, on the surface of the hub 13F facing the top plate 1Fa, so-called disk friction (frictional resistance on the surface of the rotating disk) pushes air outward in the radial direction, generating a flow R in the opposite direction to the leakage flow P. This flow R and the leakage flow P form a vortex V. As shown in FIG. 13, in the gap S between the top plate 1Fa and the hub 13F, the vortex V also exists in an area radially outward from the hub 13F. As a result, the flow of air from the centrifugal fan 10F toward the upper part of the indoor heat exchanger 6 is obstructed by the vortex V, making it difficult for air to flow to the upper part of the indoor heat exchanger 6.

[0047] In contrast, according to the first embodiment shown in FIG. 5, a portion of the air discharged radially outward from the centrifugal fan 10 is deflected toward the top plate 1a along the curved portion 13b, and this air is further guided directly to the top of the indoor heat exchanger 6 along the top plate inclined portion 1av.

[0048] In the first embodiment, a radially outward flow R caused by disc friction on the top plate 1a side of the hub 13 flows toward the top plate 1a along the curved portion 13b, and then merges with the leakage flow P from the centrifugal fan 10. As a result, a relatively small vortex V is generated at a location closer to the rotation axis Z of the centrifugal fan 10 than the end portion 131b of the curved portion 13b. Therefore, the air flow toward the upper part of the indoor heat exchanger 6 is hardly obstructed by the vortex V.

[0049] If the curved portion 13b shown in Fig. 5 is provided but the top plate inclined portion 1av is not provided, a part of the air flowing diagonally upward along the curved portion 13b is likely to separate. As a result, air is more likely to flow into the gap S between the top plate 1a and the hub 13, and the flow rate of the leakage flow P increases. If, for example, the curved portion 13b is made larger and brought closer to the top plate 1a as a measure to reduce such leakage flow P, not only will the manufacturing cost increase, but the proximity of the curved portion 13b to the indoor heat exchanger 6 may also lead to an increase in noise.

[0050] Moreover, if the top plate inclined portion 1av is provided but the curved portion 13b is not provided, most of the air discharged radially outward from the centrifugal fan 10 flows into the indoor heat exchanger 6 approximately perpendicularly. Therefore, the upper portion of the indoor heat exchanger 6 is not effectively used as an air flow path, and the average flow velocity of the air passing through the indoor heat exchanger 6 increases. As a result, the air pressure loss in the indoor heat exchanger 6 increases, and the flow rate of the air discharged from the centrifugal fan 10 decreases, leading to a decrease in the heat exchange efficiency. Moreover, if the rotation speed of the centrifugal fan 10 is increased in order to obtain the air flow rate, the noise of the centrifugal fan 10 increases.

[0051] In contrast, in the first embodiment, by providing both the curved portion 13b and the top plate inclined portion 1av, a part of the air discharged from the centrifugal fan 10 flows sequentially along the curved portion 13b and the top plate inclined portion 1av, and is led directly to the upper portion of the indoor heat exchanger 6. This ensures a sufficient flow rate of air passing through the upper portion of the indoor heat exchanger 6, improving its heat exchange performance. In addition, since the amount of heat exchanged in the indoor heat exchanger 6 is ensured without requiring a large rotation speed of the motor 11, noise associated with the driving of the centrifugal fan 10 can be reduced.

[0052] Furthermore, according to the first embodiment, by providing the top plate inclined portion 1av and the curved portion 13b, it is possible to narrow the gap S between the top plate 1a and the hub 13 without particularly changing the height position of the centrifugal fan 10. Furthermore, since the air flowing along the curved portion 13b is directly guided to the top plate inclined portion 1av, it is possible to suppress the leakage flow P. This increases the flow velocity of the air toward the upper portion of the indoor heat exchanger 6, allowing the upper portion of the indoor heat exchanger 6 to be effectively utilized.

[0053] FIG. 6 shows simulation results for the flow speed of air passing through the indoor heat exchanger under the same air volume condition in the first embodiment and the comparative example (see FIG. 5 and FIG. 13 as appropriate). The horizontal axis in FIG. 6 represents the average value of the component of the flow velocity of the air passing through the indoor heat exchanger 6 that is perpendicular to the fins 6a of the indoor heat exchanger 6 in the circumferential direction of the rotation axis Z. The vertical axis in FIG. 6 represents the value of d / H. Note that d is the vertical distance from the top end of the indoor heat exchanger 6, and H is the vertical length of the indoor heat exchanger 6. For example, at the top end of the indoor heat exchanger 6, the value of d / H is zero. On the other hand, at the bottom end of the indoor heat exchanger 6, the value of d / H is 1.

[0054] Moreover, the solid line in Fig. 6 is the simulation result for the first embodiment (see Fig. 5), while the dashed line in Fig. 6 is the simulation result for the comparative example (see Fig. 13). For example, in the comparative example (dashed line in FIG. 6) in which the curved portion 13b (see FIG. 5) and the top plate inclined portion 1av (see FIG. 5) are not provided, the component of the air flow velocity perpendicular to the indoor heat exchanger 6 has a relatively small value near the upper end of the indoor heat exchanger 6 (where the value of d / H is zero). This is because, in the configuration of the comparative example (see FIG. 13), as described above, leakage flow P into the gap S between the top plate 1Fa and the hub 13F is likely to occur, and the air flow from the centrifugal fan 10F toward the upper part of the indoor heat exchanger 6 is obstructed by the vortex V.

[0055] In contrast, in the first embodiment (solid line in FIG. 6), the component of the air flow velocity perpendicular to the indoor heat exchanger 6 near the upper end of the indoor heat exchanger 6 is about 14% larger than that of the comparative example, assuming that it is 100%. As described above, in the configuration of the first embodiment (see FIG. 5), part of the air discharged from the centrifugal fan 10 flows sequentially along the curved portion 13b and the top plate inclined portion 1av, and is led directly to the upper part of the indoor heat exchanger 6.

[0056] In Fig. 6, when the value of d / H is in the range of 0.2 to 1, the component of the air flow velocity perpendicular to the indoor heat exchanger 6 is slightly larger in the comparative example (dashed line) than in the first embodiment (solid line). However, as a result of performing a steady-state analysis with the rotation speed of the motor 11 of the centrifugal fan 10 kept constant, the air volume increased by 0.8% and the APF (Annual Performance Factor) increased by +0.2% in the first embodiment compared to the comparative example. In other words, the result was obtained that the flow rate of air passing through the entire indoor heat exchanger 6 is larger in the first embodiment than in the comparative example.

[0057] Furthermore, when the rotation speed of the motor 11 was adjusted so that the air volume was approximately the same in the first embodiment and the comparative example, the noise level of the centrifugal fan 10 in the first embodiment was reduced by 0.2 [dB] compared to the comparative example. Thus, according to the first embodiment, it is possible to provide an indoor unit 100 that has high heat exchange performance and energy saving properties and is quiet.

[0058] Second Embodiment The second embodiment (see FIG. 7) differs from the first embodiment (see FIG. 5) in that the inclined surface G2 of the tabletop inclined portion 1Aav is curved rather than flat. Note that the configuration other than the tabletop inclined portion 1Aav is the same as that of the first embodiment. Therefore, only the parts that are different from the first embodiment will be described, and the description of the overlapping parts will be omitted.

[0059] FIG. 7 is a partial enlarged view of the indoor unit 100A of the air conditioner according to the second embodiment, cut in vertical section. As shown in FIG. 7, the top plate 1Aa of the housing 1A includes a plate-shaped portion 1au, a top plate inclined portion 1Aav, and a thick portion 1aw. The inclined surface G2 of the top plate inclined portion 1Aav is curved in a predetermined manner so that the closer it is to the indoor heat exchanger 6 in the horizontal direction, the higher its height position becomes. In the example of FIG. 7, the inclined surface G2 of the top plate inclined portion 1Aav has an upwardly convex curved shape in a vertical cross-sectional view. An example of such a curved shape is a predetermined arc whose center of curvature (not shown) is located below the top plate 1Aa and passes near the upper end of the indoor heat exchanger 6. Such a curved surface configuration is also included in the term "inclined surface."

[0060] In the vertical cross section, the end 131b of the curved portion 13b is provided on the tangent Ga2 at the lower end of the inclined surface G2. As a result, the air flowing obliquely upward along the curved portion 13b is guided directly to the upper part of the indoor heat exchanger 6 along the inclined surface G2 of the top plate inclined portion 1Aav. Note that the fact that the end 131b of the curved portion 13b is provided on the tangent Ga2 at the lower end of the inclined surface G2 is included in the fact that the end 131b of the curved portion 13b is provided on the extension line of the inclined surface G2.

[0061] <Effects> According to the second embodiment, the inclined surface G2 of the top plate inclined portion 1Aav has an upwardly convex curved shape in a vertical cross section, so that the air flowing along the inclined surface G2 flows in at an angle close to perpendicular to the fins 6a of the indoor heat exchanger 6. Therefore, the proportion of the component perpendicular to the fins 6a of the indoor heat exchanger 6 in the flow velocity of the air passing over the upper part of the indoor heat exchanger 6 becomes large. As a result, the heat exchange efficiency of the indoor heat exchanger 6 can be further improved compared to the first embodiment.

[0062] Third Embodiment The third embodiment (see FIG. 8) differs from the first embodiment in that the inclination angle of the inclined surface G3 in the tabletop inclined portion 1av varies in the circumferential direction of the rotation axis Z. The rest of the third embodiment is similar to the first embodiment. Therefore, only the parts that differ from the first embodiment will be described, and the description of the overlapping parts will be omitted.

[0063] FIG. 8 is a vertical cross-sectional view of the indoor unit 100 of the air conditioner according to the third embodiment, taken along line III-III in FIG. As described above, the indoor heat exchanger 6 provided in the indoor unit 100 has a rectangular frame shape with rounded corners in cross section (see FIG. 3). On the other hand, the hub 13 of the centrifugal fan 10 has a circular shape in cross section. Therefore, the horizontal distance between the end 131b of the curved portion 13b of the hub 13 and the indoor heat exchanger 6 varies in the circumferential direction of the rotation axis Z (see FIG. 4). Note that the vertical cross section of the indoor unit 100 of the air conditioner according to the third embodiment taken along line II-II in FIG. 3 has the same configuration as FIG. 5 used in the description of the first embodiment.

[0064] That is, in the indoor heat exchanger 6 having a rectangular frame shape in cross section, near the midpoints of each of the four sides (cross section II-II in FIG. 3), the horizontal distance L1 between the end 131b of the curved portion 13b and the indoor heat exchanger 6 is relatively short, as shown in Fig. 5. On the other hand, in the indoor heat exchanger 6 having a rectangular frame shape in cross section, near the four rounded corners (cross section III-III in FIG. 3), the horizontal distance L2 between the end 131b of the curved portion 13b and the indoor heat exchanger 6 is relatively long, as shown in Fig. 8.

[0065] In this way, in the vertical cross section, the inclination angle of the inclined surface G3 with respect to the lower surface of the plate-shaped portion 1au (predetermined plane F1 perpendicular to the rotation axis Z) varies in the circumferential direction of the rotation axis Z (see FIG. 4). Specifically, the inclination angle of the inclined surface G3 is smaller (θ1>θ2) at a location where the lateral distance between the end 131b of the curved portion 13b and the indoor heat exchanger 6 is long (see FIG. 8) than at a location where this distance is short (see FIG. 5).

[0066] As a result, even in a portion where the lateral distance between the curved portion 13b and the indoor heat exchanger 6 is relatively long (see FIG. 8), the air flowing through the curved portion 13b is guided directly to the upper portion of the indoor heat exchanger 6 along the inclined surface G3 of the top plate inclined portion 1av. Therefore, a sufficient flow rate of air passing over the upper portion of the indoor heat exchanger 6 can be ensured over almost the entire circumferential direction of the rotation axis Z (see FIG. 4). Note that the inclination angle θ2 of the inclined surface G3 may be smoothly changed in the circumferential direction of the rotation axis Z (see FIG. 4).

[0067] In addition, in the indoor heat exchanger 6 (see FIG. 3) that has a rectangular frame shape in cross section, even near the four rounded corners (cross section III-III in FIG. 3), it is preferable that the point J3 where the height position of the inclined surface G3 is highest is close to the indoor heat exchanger 6. This makes it easier for the air flowing along the inclined surface G3 of the top plate inclined portion 1av to be guided to the upper part of the indoor heat exchanger 6.

[0068] <Effects> According to the third embodiment, even if the lateral distance between the curved portion 13b and the indoor heat exchanger 6 varies in the circumferential direction of the rotation axis Z (see FIG. 4), the air discharged from the centrifugal fan 10 is guided along the inclined surface G3 to the upper part of the indoor heat exchanger 6 over almost the entire area in the circumferential direction. Therefore, the heat exchange performance of the indoor unit 100 can be improved.

[0069] Fourth Embodiment The fourth embodiment differs from the first embodiment in that the ratio of the vertical length ΔL of the outlet port of the centrifugal fan 10 (see FIG. 4) to the vertical length H of the indoor heat exchanger 6 (see FIG. 4) is within a predetermined range. The rest of the fourth embodiment is similar to the first embodiment. Therefore, only the parts that differ from the first embodiment will be described, and the description of the overlapping parts will be omitted.

[0070] FIG. 9 shows the results of a simulation showing the relationship between the value of ΔL / H and the volume of air passing through the indoor heat exchanger in the indoor unit of the air conditioner according to the fourth embodiment (see FIGS. 4 and 5 as appropriate). The horizontal axis in Fig. 9 is the value of ΔL / H. Here, ΔL is the difference in height between the end 131b of the curved portion 13b (see Fig. 5) and the radially outer edge of the shroud 14 (see Fig. 4). Also, H is the vertical length of the indoor heat exchanger 6. Also, the vertical axis in Fig. 9 is the volume of air discharged from the centrifugal fan 10.

[0071] 9, the simulation was performed with the rotation speed of the centrifugal fan 10 constant, the height position of the hub 13 fixed, and the height position of the shroud 14 changed as required. Note that when the vertical length ΔL of the outlet port of the centrifugal fan 10 is reduced, the ratio ΔL / H also decreases accordingly.

[0072] If the ratio ΔL / H is too small, friction loss inside the centrifugal fan 10 increases, reducing the air volume of the centrifugal fan 10. On the other hand, if the ratio ΔL / H is too large, the vertical length of the flow passage between the hub 13 and the shroud 14 increases, causing the air sucked into the centrifugal fan 10 to separate from the shroud 14, reducing the efficiency of the centrifugal fan 10.

[0073] In other words, if the value of the ratio ΔL / H is too large or too small, the air volume of the centrifugal fan 10 decreases and the heat exchange efficiency of the indoor heat exchanger 6 decreases. Here, the simulation results show that the air volume discharged from the centrifugal fan 10 is particularly high within the range of 0.42≦ΔL / H≦0.46 (the range indicated by dots in FIG. 9). Therefore, it is preferable that the ratio ΔL / H has the relationship of 0.42≦ΔL / H≦0.46. This makes it possible to suppress the friction loss inside the centrifugal fan 10 while suppressing the separation of air from the shroud 14, thereby enabling the centrifugal fan 10 to be driven with high efficiency.

[0074] <Effects> According to the fourth embodiment, by setting the magnitude of the ratio ΔL / H within the range of 0.42≦ΔL / H≦0.46, the centrifugal fan 10 can be driven with high efficiency, and thus the power consumption of the air conditioner W1 can be reduced. In addition, since the rotation speed of the centrifugal fan 10 when obtaining a predetermined air volume can be relatively low, noise associated with the driving of the centrifugal fan 10 can be suppressed.

[0075] <<Variations>> While the indoor unit 100 of the air conditioner W1 according to the present invention and the like have been described in each embodiment above, the present invention is not limited to these descriptions and various modifications can be made. For example, in the first embodiment (see FIG. 5), a corner (obtuse corner) is formed between the inclined surface G1 of the top plate inclined portion 1av and the lower surface of the thick portion 1aw, but the present invention is not limited to this. For example, the configuration shown in FIG. 10 described next may be used.

[0076] FIG. 10 is a vertical cross-sectional view of an indoor unit 100B of an air conditioner according to a first modified example. In the example of Fig. 10, R-chamfering is performed near the lower end of the inclined surface G4 of the inclined portion 1Bav of the tabletop. In such a configuration, the end 131b of the curved portion 13b may be provided on an extension line Ga4 of the inclined surface G4 of the tabletop inclined portion 1Bav in a vertical cross section. Here, the "extension line" of the inclined surface G4 means a straight line extended from the lower end M4 (just before the R-chamfered portion) of the part of the inclined surface G4 that is linear in a vertical cross section. Furthermore, the end 131b of the curved portion 13b may be provided on a tangent to the lower end M4 of the inclined surface G4. Here, the "tangent" to the lower end of the inclined surface G4 means a tangent to the lower end M4 (immediately before the R-chamfered portion) of the linear portion of the inclined surface G4 in a vertical cross-sectional view.

[0077] In each embodiment, the configuration has been described in which the extension line Ga1 of the inclined surface G1 of the inclined portion 1av (see FIG. 5) passes through the lower surface of the end 131b of the curved portion 13b in the vertical cross section, but this is not limited thereto. That is, the extension line Ga1 of the inclined surface G1 of the inclined portion 1av of the table top may pass between the upper and lower surfaces of the end 131b of the curved portion 13b, or may pass through the upper surface of the end 131b of the curved portion 13b. Such a configuration is also included in the matter that the end 131b of the curved portion 13b is provided on the extension line Ga1 of the inclined surface G1 in the vertical cross section.

[0078] Also, the end 131b of the curved portion 13b (see FIG. 5) may have a rounded shape in vertical cross section. In such a configuration, the extension line Ga1 of the inclined surface G1 of the tabletop inclined portion 1av passing through the end 131b of the curved portion 13b means that the extension line Ga1 of the inclined surface G1 passes through a predetermined point included in the rounded end 13b (a curved line that is an arc in vertical cross section).

[0079] In addition, in each embodiment, a case has been described in which the end 131b of the curved portion 13b is provided on the extension line Ga1 of the inclined surface G1 of the tabletop inclined portion 1av (see Figure 5), but this is not limited to this and may be, for example, as shown in Figure 11.

[0080] FIG. 11 is a vertical cross-sectional view of an indoor unit of an air conditioner according to a second modified example. In addition, FIG. 11 shows a configuration similar to that of the first embodiment (see FIG. 5), but the positional relationship between the tabletop inclined portion 1av and the curved portion 13b is specified from another viewpoint as follows. That is, in a vertical cross section, the inner edge N1 (edge ​​on the rotation axis side) of the inclined surface G1 of the tabletop inclined portion 1av may be provided on the tangent T1 of the end 131b of the curved portion 13b. Here, "on the tangent" of the end 131b of the curved portion 13b is not limited to "on the tangent" in the strict sense. For example, the term "on the tangent" of the end 131b of the curved portion 13b also includes a range of ±10° or less in a vertical cross section based on the tangent T1 of the end 131b of the curved portion 13b.

[0081] 11 shows a configuration in which the inner edge N1 of the inclined surface G1 is provided on the tangent line T1 of the lower surface of the end 131b of the curved portion 13b in the vertical cross section, but this is not limited thereto. For example, the inner edge N1 of the inclined surface G1 may be provided on the tangent line of the upper surface of the end 131b of the curved portion 13b. 11, the inner edge of the inclined surface G1 may be rounded. In this configuration, the inner edge of the inclined surface G1 (the edge on the rotating shaft side) is the lower end of the linear portion of the inclined surface G1 in a vertical cross section (immediately before the rounded portion).

[0082] In each embodiment, the thickness of the thick portion 1aw of the top plate 1a (see FIG. 5) in the vertical direction is generally constant throughout the entire radially inner area of ​​the top plate 1a, but this is not limited thereto. That is, the thickness of the thick portion 1aw in the vertical direction may differ in a predetermined manner depending on the position of the thick portion 1aw.

[0083] In addition, in each embodiment, a configuration has been described in which the upper end of the top plate inclined portion 1av (see FIG. 5) is close to the indoor heat exchanger 6, but this is not limited thereto. That is, the upper end of the top plate inclined portion 1av may be relatively far away (for example, several centimeters or more) from the indoor heat exchanger 6. In such a configuration, the inclination angle of the inclined surface G1 of the top plate inclined portion 1av (see FIG. 5) may be approximately constant in the circumferential direction of the rotation axis Z, or the inclination angle may vary by a predetermined amount in the circumferential direction.

[0084] In the second embodiment (see FIG. 7), the inclined surface G2 of the tabletop inclined portion 1Aav is configured to have an upwardly convex curved shape in a vertical cross section, but this is not limited thereto. For example, the upper part of the inclined surface G2 may be configured to have an upwardly convex curved shape in a vertical cross section, while the lower part of the inclined surface G2 may be configured to have a downwardly convex curved shape. In such a configuration, the lower part of the inclined surface G2 may be subjected to R-chamfering. Note that the "extension line" and "tangent line" when the lower part of the inclined surface G2 is subjected to R-chamfering are as described above.

[0085] In the third embodiment (see FIG. 8), the inclined surface G3 of the tabletop inclined portion 1av is linear in a vertical cross section over the entire circumferential area of ​​the rotation axis Z, but this is not limiting. That is, the inclined surface G3 of the tabletop inclined portion 1av may be linear in a vertical cross section over a predetermined range in the circumferential area of ​​the rotation axis Z, while the inclined surface G3 may be curved in a vertical cross section over another range. With this configuration, the same effect as the third embodiment can be achieved.

[0086] In addition, each embodiment, the first modified example, and the second modified example can be appropriately combined. For example, the first embodiment (see FIG. 1) and the fourth embodiment (see FIG. 9) may be combined to form the following configuration. That is, in a configuration in which the end 131b of the curved portion 13b is provided on the extension line Ga1 of the inclined surface G1 in a vertical cross-sectional view (first embodiment), the magnitude of the ratio ΔL / H may be within a range of 0.42≦ΔL / H≦0.46 (fourth embodiment). Also, for example, the second embodiment (see FIG. 7) and the third embodiment (see FIG. 8) may be combined to form a configuration in which the inclined surface G2 of the tabletop inclined portion 1Aav is curved (second embodiment), so that the inclination angle of the inclined surface G2 may be different in a predetermined manner in the circumferential direction (third embodiment). Other combinations are also possible.

[0087] In addition, in each embodiment, a configuration has been described in which the multi-type air conditioner W1 (see FIG. 1) is equipped with four indoor units 100, but this is not limited to the above. That is, the number of indoor units 100 may be one, or a configuration in which multiple indoor units are connected in parallel. Also, multiple outdoor units 200 connected in parallel may be provided.

[0088] In addition, each embodiment is described in detail to easily explain the present invention, and is not necessarily limited to having all of the configurations described. In addition, a part of the configuration of each embodiment can be replaced with the configuration of another embodiment. In addition, a configuration of another embodiment can be added to a configuration of an embodiment as appropriate. Other configurations can be added, deleted, or replaced with respect to a part of the configuration of each embodiment. In addition, the above-mentioned mechanisms and configurations are those considered necessary for explanation, and do not necessarily show all mechanisms and configurations in a product. [Explanation of symbols]

[0089] 1 Case 1a, 1Aa Top plate 1au Plate-shaped part 1av, 1Aav, 1Bav Top plate inclination 1aw thick part 1b side plate 6 Indoor heat exchanger 10. Centrifugal Fan 11 Motor 12 Feather 13. Hub 13a base 13b Curved section 131b End 14 Shroud 100,100A,100B indoor unit 200 outdoor unit F1 plane G1,G2,G3,G4 Inclined surface Ga1,Ga4 extension line Ga2 tangent J1 Location J3 Location N1 Edge T1 tangent W1 Air conditioner Z Rotation Axis

Claims

1. A housing having a top panel and a side panel; a centrifugal fan accommodated in the housing; an indoor heat exchanger disposed within the housing so as to surround the centrifugal fan; The centrifugal fan is A motor as a drive source; A plurality of blades arranged at predetermined intervals in a circumferential direction; a hub that is disposed on the top plate side of the plurality of blades and is disposed on a rotating shaft of the motor; a shroud disposed on the opposite side of the blades from the top plate, The hub has a curved portion that is curved toward the top plate on a radially outer side of the plurality of blades, The top plate has a top plate inclined portion including an inclined surface inclined so that the height position becomes higher as the top plate is closer to the indoor heat exchanger in the horizontal direction, and a thick portion provided over the entire inner area of ​​the top plate inclined portion, The thick portion is also provided directly above the motor, The thick portion has a flat surface facing the hub. a thickness of the thick portion in the vertical direction is constant in the radial direction and the circumferential direction of the rotation shaft of the motor, and is equal to a difference in height position from the upper end to the lower end of the inclined top plate portion; A vertical cross section of a portion including the top plate inclined portion and the thick portion has a trapezoidal shape with the inclined surfaces as a pair of legs, The top plate inclined portion is provided on the inner side of the indoor heat exchanger in a radial direction of the rotation shaft, An indoor unit for an air conditioner, wherein, in a vertical cross-sectional view, an end of the curved portion is provided on an extension line of the inclined surface.

2. In a vertical cross-sectional view, the inclined surface is curved, and the end of the curved portion is provided on a tangent line at a lower end of the inclined surface.

2. The indoor unit of an air conditioner according to claim 1 .

3. In a vertical cross-sectional view, the highest point of the inclined surface is adjacent to the indoor heat exchanger.

2. The indoor unit of an air conditioner according to claim 1 .

4. In a vertical cross-sectional view, an inclination angle of the inclined surface with respect to a predetermined plane perpendicular to the rotation shaft varies in a circumferential direction of the rotation shaft, The inclination angle of the inclined surface is smaller at a portion where the lateral distance between the end of the curved portion and the indoor heat exchanger is long than at a portion where the lateral distance is short.

4. The indoor unit of an air conditioner according to claim 3.

5. In the radial direction of the rotation axis, the lower surface of the tabletop in an inner region of the tabletop inclination portion is lower in height than the lower surface of the tabletop in an outer region of the tabletop inclination portion.

2. The indoor unit of an air conditioner according to claim 1 .

6. When the difference in height between the end of the curved portion and the radially outer edge of the shroud is ΔL and the length of the indoor heat exchanger in the vertical direction is H, 0.42≦ΔL / H≦0 . 46 relationships are established The indoor unit of an air conditioner according to any one of claims 1 to 5,

7. A housing having a top panel and a side panel; a centrifugal fan accommodated in the housing; an indoor heat exchanger disposed within the housing so as to surround the centrifugal fan; The centrifugal fan is A motor as a drive source; A plurality of blades arranged at predetermined intervals in a circumferential direction; a hub that is disposed on the top plate side of the plurality of blades and is disposed on a rotating shaft of the motor; a shroud disposed on the opposite side of the blades from the top plate, The hub has a curved portion that is curved toward the top plate on a radially outer side of the plurality of blades, The top plate has a top plate inclined portion including an inclined surface inclined so that the height position becomes higher as the top plate is closer to the indoor heat exchanger in the horizontal direction, and a thick portion provided over the entire inner area of ​​the top plate inclined portion, The thick portion is also provided directly above the motor, The thick portion has a flat surface facing the hub. a thickness of the thick portion in the vertical direction is constant in the radial direction and the circumferential direction of the rotation shaft of the motor, and is equal to a difference in height position from the upper end to the lower end of the inclined top plate portion; A vertical cross section of a portion including the top plate inclined portion and the thick portion has a trapezoidal shape with the inclined surfaces as a pair of legs, The top plate inclined portion is provided on the inner side of the indoor heat exchanger in a radial direction of the rotation shaft, An indoor unit for an air conditioner, wherein, in a vertical cross section, an edge of the inclined surface on the side of the rotation shaft is provided on a tangent to an end of the curved portion.

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