WO2023286208A1

WO2023286208A1 - Indoor unit and air conditioner

Info

Publication number: WO2023286208A1
Application number: PCT/JP2021/026475
Authority: WO
Inventors: 美優中野; 健一迫田; 皓亮宮脇; 翔太森川; 誠谷島
Original assignee: 三菱電機株式会社
Priority date: 2021-07-14
Filing date: 2021-07-14
Publication date: 2023-01-19
Also published as: JPWO2023286208A1; JP7357827B2

Abstract

The present invention can provide an indoor unit and an air conditioner having improved blowing efficiency while ensuring a heat exchange capacity even when the indoor unit is reduced in size. An indoor unit (1) is provided with: a housing (2); a centrifugal blower (4) having an impeller (5), and a spiral casing (6) provided with a wall surface (12) and a side surface (13); and, a heat exchanger (3) for surrounding the periphery of the wall surface by having a curved shape as a whole. The spiral casing (6) has a connection section (15) for connecting the wall surface and the side surface in a chamfered shape. When the angle around the rotational axis is expressed as a rotation angle θ, the distance between the wall surface and the heat exchanger as a radial distance LH, and the length of the wall surface in the direction of the rotational axis as Hc, the heat exchanger (3) is disposed so that LH varies according to the rotation angle θ, and the length Hc of the wall surface in the direction of the rotational axis at a rotation angle θ at which LH is short is shorter than the length Hc of the wall surface in the direction of the rotational axis at a rotation angle θ at which LH is long. An air conditioner (30) is provided with the indoor unit (1) and an outdoor unit (31).

Description

Indoor unit and air conditioner

The present disclosure relates to indoor units and air conditioners.

In an indoor unit, a flat plate-shaped heat exchanger is installed on the suction port side of the body casing so as to face the suction port of the body casing, and a notch is formed on the opposite side of the air outlet of the spiral casing. machine is known (Patent Document 1).

Japanese Patent Application Laid-Open No. 2004-347311

Securing heat exchange capacity has become a problem as indoor units have become smaller. Although Patent Literature 1 refers to miniaturization of the indoor unit, the size of the heat exchanger is limited, and sufficient heat exchange capacity is not taken into consideration.

The present disclosure has been made in order to solve the above-described problems, and an indoor unit and an air conditioner that improve ventilation efficiency while ensuring heat exchange capacity even when the indoor unit is downsized. The purpose is to provide a harmonizing machine.

An indoor unit according to the present disclosure includes a housing having a main body inlet and a main body outlet, a main plate provided inside the housing and rotating around a rotation axis, and a plurality of blades arranged on the main plate. A centrifugal blower having a wheel, a spiral casing having a wall surface spirally surrounding the periphery of the impeller and a side surface formed with a suction port for the impeller to suck in air; and a heat exchanger that surrounds the periphery of the wall surface by having a curved shape as, the angle around the rotation axis is the rotation angle θ, the distance between the wall surface and the heat exchanger is the radial distance LH, and the wall surface The heat exchanger is arranged so that the radial distance LH varies depending on the rotation angle θ. and the length Hc of the wall surface in the rotation axis direction at the rotation angle θ at which the radial distance LH is short is shorter than the length Hc of the wall surface in the rotation axis direction at the rotation angle θ at which the radial distance LH is long. Further, an air conditioner according to the present disclosure includes the indoor unit and the outdoor unit.

According to the present disclosure, it is possible to provide an indoor unit and an air conditioner that improve air blowing efficiency while ensuring heat exchange capacity even when the indoor unit is downsized.

1 is a perspective view showing an indoor unit according to Embodiment 1; FIG. Fig. 2 is a perspective view of the interior of the indoor unit according to the first embodiment; Fig. 3 is a cross-sectional view of the main part inside the indoor unit according to the first embodiment; 1 is a perspective view of a centrifugal fan according to Embodiment 1; FIG. Fig. 2 is a plan view of the spiral casing according to the first embodiment, viewed from the suction port side; FIG. 5 is a diagram showing the relationship between the radial distance with respect to the rotation angle θ and the length of the wall surface in the rotation axis direction according to the first embodiment; FIG. 3 is a schematic diagram showing the flow of air taken in by the indoor unit according to the first embodiment; FIG. 4 is a perspective view of the interior of an indoor unit according to a modification of the first embodiment; FIG. 8 is a perspective view of the interior of the indoor unit according to the second embodiment; FIG. 10 is a plan view of the spiral casing according to the second embodiment, viewed from the suction port side; FIG. 8 is a plan view of the interior of the indoor unit according to the second embodiment, viewed from the rear side; FIG. 9 is a schematic diagram showing the flow of air drawn into the indoor unit when viewed from the side of the spiral casing according to the second embodiment; FIG. 8 is a schematic diagram showing the flow of air taken in by the indoor unit when the interior of the indoor unit according to the second embodiment is viewed from the back side; FIG. 11 is a perspective view of the inside of an indoor unit according to Embodiment 3; FIG. 11 is a plan view of the spiral casing according to the third embodiment, viewed from the suction port side; FIG. 15 is a cross-sectional view taken along line AA of FIG. 14; FIG. 16 is a schematic diagram showing the flow of air sucked into the indoor unit in the cross section of FIG. 15; FIG. 11 is a perspective view of the inside of an indoor unit according to Embodiment 4; FIG. 11 is a plan view of the spiral casing according to the fourth embodiment, viewed from the suction port side; FIG. 12 is a schematic diagram showing the flow of air taken in by the indoor unit when viewed from the side of the spiral casing according to the fourth embodiment; FIG. 11 is a circuit diagram showing an air conditioner according to Embodiment 5;

First, an embodiment of the present disclosure will be described with reference to the drawings. In each drawing, the same reference numerals are the same or equivalent, and this is common throughout the specification. In addition, the constituent elements shown in the full text of the specification are merely examples, and the present invention is not limited to these descriptions.

Embodiment 1.
FIG. 1 is a perspective view showing an indoor unit according to Embodiment 1. FIG. As shown in FIG. 1 , the indoor unit 1 has a housing 2 and a heat exchanger 3 and a centrifugal fan 4 inside the housing 2 . A main body suction port 2a is provided in the upper part of the housing 2, and a main body outlet 2b is provided in the lower part of the housing 2. - 特許庁The body suction port 2a is an opening for taking in air from the outside of the housing to the inside of the housing. The body outlet 2b is an opening for blowing out the air heat-exchanged in the housing to the outside of the housing.

FIG. 2 is a perspective view of the interior of the indoor unit with the housing 2 removed from FIG. The centrifugal blower 4 draws air into the housing and creates an air flow that blows out the heat-exchanged air to the outside of the housing. Centrifugal blower 4 has impeller 5 and spiral casing 6 . As shown in FIG. 2, two or more centrifugal blowers 4 are arranged at predetermined intervals along a rotating shaft 8 connected to a drive motor 7 . The impeller 5 is rotated by the drive motor 7, and the centrifugal force generated by the rotation blows air in the radial direction of the impeller 5. As shown in FIG.

　Fig. 3 is a cross-sectional view of the main part inside the indoor unit. As shown in FIG. 3 , the impeller 5 has a main plate 9 and a plurality of blades 10 attached to both sides of the main plate 9 . The main plate 9 is a disc rotatably mounted around the rotation axis 8 . A plurality of blades 10 are arranged on the circumference of the main plate 9 at predetermined intervals from each other. One end of the blade 10 is fixed to the main plate 9 so that the height direction of the blade 10 is aligned with the rotation axis direction.

Fig. 4 is a perspective view of the centrifugal blower. The spiral casing 6 is, for example, a hollow cylinder forming a space inside which air flows. The impeller 5 sucks air into the spiral casing 6 from the casing suction port 6a and blows the air radially outward. The spiral casing 6 rectifies the air blown radially outward by the impeller 5 and blows it out from the casing outlet 6b, which is the outlet of the spiral casing 6 . The spiral casing 6 includes a wall surface 12 spirally surrounding the periphery of the impeller 5 in the rotational direction of the impeller 5, a side surface 13 formed with a casing suction port 6a through which the impeller 5 sucks air, and the spiral casing 6. and a casing outlet 6b for blowing air out of the housing. The spiral casing 6 also has a bell mouth 11 for smoothing the airflow at the casing inlet 6a. The bellmouth 11 is, for example, an annular plate. The spiral casing 6 also includes tongues 14 that direct the airflow generated by the rotation of the impeller 5 toward the casing outlet 6b.

The side surfaces 13 are two end surfaces that connect with the bell mouth 11 and cover the impeller 5 . The side surface 13 forms a plane in a direction perpendicular to the rotation axis 8 . The wall surface 12 is provided so that the distance from the rotating shaft 8 increases as the angle of rotation about the rotating shaft increases toward the casing outlet 6b from the tongue portion 14 as a starting point. The wall surface 12 forms a plane parallel to the rotation axis 8 .

As shown in FIG. 4, a connection portion 15 is a portion where the wall surface 12 and the side surface 13 of the spiral casing 6 are connected. The connecting portion 15 is a curved surface chamfered so as to cut off the corners, and connects the wall surface 12 and the side surface 13 in a chamfered manner. Although FIG. 4 shows the connecting portion 15 chamfered into a half-moon shape, the chamfered shape of the connecting portion 15 is not limited to this. Moreover, the connection part 15 is provided so that the connection part 15 and the wall surface 12 may continue. By providing the connecting portion 15 so as to be continuous, the air that has passed through the heat exchanger 3 can smoothly flow along the curved surface of the connecting portion 15 to the casing suction port 6a. In addition, by chamfering the corners of the wall surface 12 and the side surface 13 of the spiral casing, it is possible to suppress turbulence of the air due to the vortices formed at the corners in the flow path inside the spiral casing, thereby improving the air blowing efficiency. An improvement and noise reduction effect are also obtained.

Also, as shown in FIG. 3, the distance between adjacent spiral casings is defined as Lc, and the length of the wall surface 12 of the spiral casing in the direction of the rotation axis is defined as the length of the wall surface in the direction of the rotation axis Hc. The distance Lc between adjacent casings refers to the distance between the side surfaces of the spiral casings of two centrifugal fans 4 adjacent in the rotation axis direction.

Since the length Hc of the wall surface 12 in the rotation axis direction varies depending on the size of the connection portion 15, if the connection portion 15 is chamfered larger, the length Hc of the wall surface in the rotation axis direction becomes shorter. If the wall surface 12 is formed small, the length Hc of the wall surface 12 in the rotation axis direction becomes long. A plurality of centrifugal blowers 4 arranged along the rotation axis direction at a predetermined interval maintains the distance between the connecting portions between adjacent spiral casings by adjusting the length Hc of the wall surface 12 in the rotation axis direction. spreads.

FIG. 5 is a plan view seen from the side of the casing suction port 6a. In order to make the housing 2 compact, the heat exchanger 3 is arranged close to the centrifugal blower 4 inside the housing. As shown in FIG. 5 , the heat exchanger 3 is located upstream of the centrifugal blower 4 inside the housing, and has a curved shape as a whole to surround the wall surface 12 and to separate the wall surface 12 from the heat exchanger 3 . They are arranged so that the distance changes.

Here, the radial distance between the heat exchanger 3 and the wall surface 12 in the radial direction of the rotating shaft 8 is defined as the radial distance _LH , the angle around the rotating shaft 8 is defined as the rotation angle θ, and the spiral casing 6 The tongue portion 14 at the start of winding is set to θ=0°. The radial distance _LH refers to the distance from the outer peripheral surface of the wall surface 12 to the heat exchanger 3 facing the outer peripheral surface in a cross section of the indoor unit 1 perpendicular to the rotation axis. Arranging the heat exchanger 3 so that it has a curved shape as a whole, surrounds the periphery of the wall surface, and changes the radial distance _LH means, for example, a spiral casing having a curved outer peripheral surface as shown in FIG. is to arrange two flat plate-shaped heat exchangers 3 against the wall surface 12 of the .

Since such a flat heat exchanger 3 is installed close to the centrifugal fan 4 having a spiral outer diameter, the radial distance between the heat exchanger 3 and the wall surface 12 varies depending on the rotation angle around the rotation axis. _LH changes greatly. Moreover, the distance between the center of the rotation shaft of the centrifugal fan 4 and the heat exchanger 3 also changes greatly. Arranging the heat exchanger 3 close to the centrifugal fan 4 means that the radial distance _LH between the heat exchanger 3 and the wall surface 12 is smaller than the distance from the center of the rotation shaft to the wall surface 12. is arranged so as to have For example, the radial distance _LH between the heat exchanger 3 and the wall surface 12 is less than half the distance from the center of the rotating shaft to the wall surface 12 .

In the prior art document, one heat exchanger is provided on the casing suction port side instead of the centrifugal fan side so as to face the casing suction port, and the distance between the heat exchanger and the casing is the centrifugal fan. Longer than the distance from the center of the rotation shaft of the fan to the casing. In such a case, the heat exchange capacity cannot be secured in response to the demand for miniaturization of the housing.

On the other hand, the heat exchanger 3 according to the first embodiment has a curved shape as a whole, surrounds the periphery of the wall surface, and is arranged so that the radial distance _LH changes. Therefore, a sufficient heat exchange capacity can be secured even in response to the demand for downsizing of the housing.

Further, in the indoor unit 1 according to the first embodiment, the length Hc in the rotation axis direction of the wall surface 12 at a rotation angle with a short radial distance _LH is equal to the rotation of the wall surface 12 at a rotation angle with a long radial distance _LH . shorter than the axial length Hc. That is, the connecting portion 15 is provided such that the shorter the radial distance _LH in the rotation angle, the shorter the length Hc of the wall surface 12 in the axial direction of rotation. For example, at a rotation angle at which the heat exchanger 3 is arranged close to the spiral casing 6, the connection is made so that the length Hc of the wall surface 12 of the spiral casing in the direction of the rotation axis is shorter than at other rotation angles. The chamfer of portion 15 is sized.

Further, the heat exchanger 3 according to Embodiment 1 is arranged so that the heat exchanger 3 has two portions close to the wall surface 12 of the spiral casing. For example, as shown in FIG.
The heat exchangers 3 are arranged in the ranges of angles θ ₀ ≤ θ ≤ θ ₁ and θ ₂ ≤ θ ≤ θ ₃ around the rotating shaft 8 so that the two heat exchangers 3 form an inverted V shape. The two heat exchangers 3 are arranged such that, in a cross section taken along a plane perpendicular to the rotation shaft 8, one end of each of the first heat exchanger 3a and the second heat exchanger 3b approaches each other. are arranged at an angle to each other such that the A centrifugal blower 4 is arranged between the other ends of the first heat exchanger 3a and the second heat exchanger 3b. Thereby, the radial distance _LH can be changed between the location where the heat exchanger 3 is close to the spiral casing and the location where it is not. Also, the heat exchanger as a whole is curved around the rotating shaft 8, and the heat exchanger 3 surrounds the outside of the centrifugal blower 4. As shown in FIG. If the total angles θ ₀ ≤ θ ≤ θ ₁ and θ ₂ ≤ θ ≤ θ ₃ that each heat exchanger 3 occupies around the rotating shaft 8 are 120° or more, preferably 150° or more. good. By arranging the heat exchangers in this way, it is possible to reduce the size of the housing while ensuring the heat exchange capacity.

Here, the relationship in which the radial distance _LH changes with respect to the rotation angle θ is defined as a function _LH (θ). The adjacent portion means the rotation angle at which the function _LH (θ) becomes a minimum value in the rotation angle ranges θ ₀ ≤ θ ≤ θ ₁ and θ ₂ ≤ θ ≤ θ ₃ where the heat exchanger 3 and the wall surface 12 face each other. It points to the point corresponding to θ. Note that the rotation angle θ at which the function L _H (θ) has a minimum value includes an angle of about 20° before and after θ.

FIG. 6 is a graph showing the relationship between the radial distance _LH with respect to the rotation angle .theta. and the wall surface length Hc in the rotation axis direction, using FIG. In FIG. 6, the rotation angle θ is 0° in the direction of the tongue from the rotation axis, and two downwardly convex curves (solid lines) indicate _LH of the two heat exchangers 3a and 3b. A broken line indicates Hc. For _LH , a value obtained by subtracting the distance from the center of the rotation shaft to the wall surface 12 of the spiral casing from the distance from the center of the rotation shaft to the heat exchanger 3 at the angle θ and dividing by the thickness of the heat exchanger 3 was used. When the thickness of the heat exchanger 3 changes with respect to the rotation angle θ, it is preferable to use the thickness of a typical portion such as the central portion or the average thickness. Hc indicates the axial length of the wall surface 12 based on the axial length of the spiral casing 6, that is, the distance between the side surfaces 13 at the rotation angle θ where no chamfer is formed.

Of the two downwardly convex curves in FIG. 6, the solid line with a rotation angle of 70° to 155° indicates _LH of the heat exchanger 3a located on the left side near the tongue in FIG. The solid line of ° indicates _LH of the heat exchanger 3b located on the right side near the outlet in FIG. Thus, the two heat exchangers 3a, 3b are arranged to surround the casing over a total rotation angle of about 175°.

In the heat exchanger 3a located on the left side in FIG. 5, _LH _decreases as the rotation angle increases from 70°, reaches a minimum around 100°, and further increases as the rotation angle increases. In the heat exchanger 3b located on the right side in FIG. 5, _LH _decreases as the rotation angle increases from 165°, reaches a minimum around 220°, and further increases as the rotation angle increases. The ranges where the rotation angle is less than 70°, greater than 155° and less than 165°, and greater than 255° are ranges in which the heat exchanger 3 is not arranged. Note that the range of the rotation angle θ can be changed arbitrarily.

The minimum value of _LH is smaller than the thickness of the heat exchanger 3, and the heat exchanger 3 is very close to the wall surface 12 of the spiral casing, such as 0.5 or less of the thickness of the heat exchanger 3. It indicates that it is placed as On the other hand, when the plate-shaped heat exchanger 3 is used as shown in FIG. 5, the change in _LH due to the rotation angle θ is extremely large, and the ratio between the minimum value and the maximum value is five times or more.

Hc is 1 from 0° (tongue) to around 70°, decreases from around 70°, reaches a minimum around 115°, and then increases. and becomes 1 around 155°, decreases again around 165°, reaches a minimum around 220°, then increases and becomes 1 around 255°. The change in _LH and the change in Hc due to the rotation angle θ are generally similar changes, and Hc becomes minimum at the rotation angle θ at which _LH is the minimum value. The rotation angle θ at which _LH is the minimum value and the angle at which Hc is the minimum value may deviate by about 20°.

As shown in FIG. 6, the change of _LH and _Hc with respect to the rotation angle θ resembles a quadratic function. Since it is not greatly different from the value of Hc that becomes the minimum value at the deviated rotation angle, the effect of the present disclosure can be obtained. In addition, it is difficult to match them perfectly in terms of manufacturing. In the present disclosure, if the length Hc of the wall surface in the rotation axis direction at the rotation angle θ at which the radial distance _LH is short is shorter than the length Hc of the wall surface in the rotation axis direction at the rotation angle θ at which the radial distance _LH is long means that the chamfered portion reduces Hc to the minimum value at the rotation angle θ at which the radial distance _LH is the minimum value. For example, the difference between the rotation angle θ at which _LH is the minimum value and the rotation angle θ at which Hc is the minimum value is 20° or less.

In the heat exchanger 3 according to Embodiment 1, the heat exchanger 3 and the wall surface 12 of the spiral casing are arranged on the upstream side of the centrifugal blower 4 and in the range of rotation angles at which the heat exchanger 3 and the wall surface 12 face each other. is arranged so that the function L _H (θ) of the radial distance L _H , which is the distance between , has two minimum values. Let β1 and β2 be the angles of the two minimum values, and _Hc1 and Hc2 be the lengths of the wall surface 12 in the rotation axis direction at the respective angles. The heat exchangers are arranged so that Hc1 and Hc2 at rotation angles at which θ is β1 and β2 are shorter than _each axial length Hc at θ3.

More preferably, the connecting portion 15 is provided so that the length Hc of the wall surface 12 in the rotation axis direction is minimized at the rotation angle θ at which the function L _H (θ) is minimized. The minimum value of the function L _H (θ) indicates that the heat exchanger 3 and the wall surface 12 of the spiral casing are the closest, that is, the radial distance L _H is the shortest. Therefore, the connecting portion 15 with a large chamfer is provided so that the length Hc of the wall surface 12 in the rotation axis direction is minimized at the angle at which the radial distance _LH is minimized. In order to increase the chamfer, for example, the width of the chamfer may be increased, and in the case of chamfering in a semicircular shape, the radius may be increased. The angle formed by the wall surface 12 and the side surface 13 may be rounded so that the width of the chamfer is maximized at the rotation angle at which the radial distance _LH is minimized. Note that the rotation angle θ at which the function L _H (θ) is the minimum value includes an angle of about 20° before and after θ.

More preferably, as shown in FIG. 4, the length Hc of the wall surface 12 in the direction of the rotation axis is shorter than the length Hb of the impeller 5 in the direction of the rotation axis in the range of rotation angles in which the connecting portion 15 is provided. is provided with a chamfered connecting portion 15 . For example, at the rotation angle θ at which the function L _H (θ) is the minimum value, the connection portion 15 is provided that is shorter than the length Hb of the impeller 5 in the rotation axis direction. The length Hb of the impeller 5 in the rotation axis direction is the height of the impeller 5, and is the length of the main plate and the blades attached to both surfaces of the main plate. That is, the width of the chamfer is increased so that the length Hc of the wall surface 12 in the direction of the rotation axis is shorter than the length Hb of the impeller 5 in the direction of the rotation axis at the location where the heat exchanger 3 is close to the spiral casing 6. It is preferable to provide a connecting portion 15 with a

Next, the operation of the indoor unit 1 of Embodiment 1 will be described. The impeller 5 is rotated by the drive motor 7, and the air outside the housing is taken in from the main intake port 2a. The air taken into the housing is heat-exchanged by the heat exchanger 3 arranged upstream of the centrifugal blower 4, passes through the connecting portion 15 of the spiral casing, and enters the inside of the spiral casing from the casing suction port 6a. sucked in. The sucked air acquires air volume and static pressure by rotation of the impeller 5 inside the spiral casing, and is sent out from the casing outlet 6b. The air sent out from the casing outlet 6b is sent to the outside of the housing of the indoor unit 1 from the body outlet 2b communicating with the casing outlet 6b.

When downsizing the indoor unit 1 , it is conceivable to dispose the heat exchanger 3 closer to the spiral casing 6 . For example _, when the _heat exchanger ₃ is arranged as shown in _FIG . Since the distance between the heat exchanger 3 and the wall surface 12 differs at each rotation angle, in the vicinity of the rotation angle θ at which the heat exchanger 3 and the centrifugal fan 4 are close to each other, the casing inlet 6a slows down the flow of air toward That is, when looking around the rotation axis of the centrifugal blower 4, the air flow becomes slow where the radial distance _LH is the shortest, so the air flow toward the casing suction port 6a as a whole has a velocity distribution. If the air flow is not uniform, pressure loss may occur in the flow path from the heat exchanger 3 to the casing suction port 6a, and the air blowing efficiency may decrease.

In the prior art document, a notch is simply provided on the opposite side of the blowout hole of the spiral casing, and the heat exchanger 3 is placed around the wall near the spiral casing provided with such a notch. If they are arranged so as to surround the heat exchanger 3, the distance between the heat exchanger 3 and the spiral casing is not considered.

Therefore, the indoor unit 1 according to Embodiment 1 includes a housing 2 having a main body suction port and a main body outlet 2b, and a main plate 9 provided inside the housing and rotating around a rotation shaft 8 and a main plate 9 and a spiral wall surface 12 surrounding the impeller 5 in the direction of rotation of the impeller 5, and the wall surface 12 for the impeller 5 to suck air. A centrifugal fan 4 having a spiral casing 6 provided with a side surface 13 in which a suction port 6a is formed, and a heat exchange surrounding a wall surface 12 provided inside the housing and having a curved shape as a whole. and a vessel 3. Furthermore, when the angle around the rotation axis 8 is the rotation angle θ, the distance between the wall surface 12 and the heat exchanger 3 is L _H , and the length of the wall surface 12 in the direction of the rotation axis is Hc, the heat exchanger 3 is arranged so that the radial distance _LH varies depending on the rotation angle θ, and the spiral casing 6 has a connection portion 15 that connects the wall surface 12 and the side surface 13 in a chamfered manner, and the radial distance _LH is short. The length Hc of the wall surface in the rotation axis direction at the rotation angle θ is configured to be shorter than the length Hc of the wall surface in the rotation axis direction at the rotation angle θ at which the radial distance _LH is long.

More specifically, the chamfering of the connection portion 15 with a small radial distance _LH at a rotation angle is greater than the chamfering of the connection portion 15 with a large radial distance _LH between the heat exchanger 3 and the wall surface 12 of the spiral casing. form large. As a result, the length Hc of the wall surface 12 in the rotation axis direction at the rotation angle where the radial distance _LH is short becomes shorter than the length Hc of the wall surface 12 in the rotation axis direction at the rotation angle where the radial distance _LH is long.

Therefore, with such a configuration, by providing the connection portion 15 in the spiral casing 6 according to the change in the radial distance _LH , it is possible to appropriately secure the flow path from the heat exchanger 3 to the casing suction port 6a of the spiral casing. Even in the indoor unit 1 in which the heat exchanger 3 is arranged near the centrifugal fan 4 due to the miniaturization of the housing 2, the air blowing efficiency of the indoor unit 1 can be improved while securing the heat exchange capacity.

By providing the connecting portion 15, the distance between the connecting portions becomes longer than that between the side surfaces of the adjacent spiral casings, so that the same effect as the effect obtained by widening the distance between the adjacent casings can be obtained. be done.

Also, in the range of the rotation angle between the heat exchanger 3 and the wall surface 12 facing each other upstream of the centrifugal fan 4, the function _LH (θ) of the radial distance _LH has two minimum values. By arranging the heat exchanger 3, even if the installation area of the heat exchanger is limited due to the downsizing of the housing, it is possible to improve the ventilation efficiency while ensuring sufficient heat exchange capacity. .

Further, the connection portion 15 of the spiral casing is formed only in the angle ranges θ ₀ ≤ θ ≤ θ ₁ and θ ₂ ≤ θ ≤ θ ₃ including θ where the function L _H (θ) of the radial distance L _H has a minimum value. By doing so, the flow path inside the spiral casing 6 is not unnecessarily narrowed. Therefore, even when the indoor unit 1 is downsized and the distance between the adjacent spiral casings of the centrifugal blowers 4 arranged in parallel is narrowed, both the flow path of the air suction portion and the flow path inside the spiral casing can be reduced. can be secured, pressure loss can be reduced, and air blowing efficiency can be improved.

Further, by providing the connection portion 15 so that the length Hc of the wall surface 12 in the direction of the rotational axis is minimized at θ where the function _LH (θ) of the radial distance _LH is the minimum value, the heat exchanger 3 to the casing suction port 6a. That is, at θ where the function L _H (θ) of the radial distance L _H is the minimum value, the chamfer is maximized, so that a sufficient flow path toward the casing suction port 6a can be secured and pressure loss can be reduced. Therefore, even if the heat exchanger 3 is arranged close to the centrifugal fan 4, the ventilation efficiency of the indoor unit 1 can be improved.

In addition, the chamfered connection portion 15 is provided so that the length Hc of the wall surface 12 in the direction of the rotation axis is shorter than the length Hb of the impeller 5 in the direction of the rotation axis in the range of the rotation angle in which the connection portion 15 is provided. As a result, the pressure loss can be further reduced in the flow path from the heat exchanger 3 to the casing suction port 6a. Therefore, even if the heat exchanger 3 is arranged close to the centrifugal blower 4, the blowing efficiency of the indoor unit 1 can be further improved.

In the heat exchanger 3 according to the first embodiment, if the distance from the wall surface 12 of the spiral casing whose outer peripheral surface draws a curve changes in the rotation direction of the rotating shaft 8, the heat exchanger 3 surrounds the spiral casing. Therefore, as shown in FIG. 8, one heat exchanger 3 may be folded and arranged.

Further, when the heat exchanger 3 according to the first embodiment is located upstream of the centrifugal fan 4 and at a position where the distance from the wall surface 12 changes, and there are two adjacent locations , the number of adjacent positions is not limited to two, and may be two or more. That is, the function L _H (θ) may have two or more local minimum values.

In addition, in a configuration in which the heat exchanger 3 has a plurality of proximate points and surrounds the spiral casing 6, one proximate point has a greater distance (diameter) between the heat exchanger 3 and the spiral casing 6 than the other proximate points. When installed so that the directional distance L _H ) is apart, the chamfer at the location where the radial distance L _H is apart is small, that is, the length Hc of the wall surface in the direction of the rotation axis is longer than at other locations. You may do so.

In addition, when one of the plurality of adjacent locations is sufficiently separated from the heat exchanger 3 and the spiral casing (radial distance L _H ), the chamfer is not provided at that location and the other locations are chamfered. Only the chamfer may be provided.

Further, when there are a plurality of adjacent portions, even if the chamfering at the position farther from the tongue portion 14 is larger than the chamfering at the position closer to the tongue portion 14 in terms of rotation angle, that is, the length Hc of the wall surface in the direction of the rotation axis is shortened. good. In particular, when the rotation angle of the tongue is 0°, the heat exchanger may be installed so that there is a position close to the rotation angle larger than 180°, which is the opposite, and the chamfer at that position may be the largest. . That is, the length Hc of the wall surface in the direction of rotation axis at the rotation angle smaller than 180° may be shorter than the length Hc of the wall surface in the direction of rotation axis at the rotation angle larger than 180°. . Since the radial distance between the blades 10 and the wall surface 12 is larger at positions with large rotation angles than at positions with small rotation angles, even if such a large chamfer is formed, the wind inside the spiral casing will not be affected. flow loss can be small.

Further, the length Hc of the wall surface in the rotation axis direction according to Embodiment 1 is shortened by forming the chamfered portion of the connecting portion 15, but the portion where the chamfered portion is not formed by, for example, inclining the entire side surface 13 has the length Hc. may vary in length. Moreover, although an example in which the angle range in which the chamfered portion is formed substantially matches the angle range in which the heat exchanger 3 is formed has been shown, the angle range in which the heat exchanger 3 is formed is slightly narrower or wider. A chamfer may be formed in the range.

Embodiment 2.
The indoor unit 1 according to Embodiment 2 of the present disclosure will be described with reference to FIGS. 9 to 13. FIG. The indoor unit 1 according to the second embodiment is obtained by further providing a guide plate 16 to the indoor unit 1 according to the first embodiment. The description of the configuration that overlaps with that of the first embodiment is omitted, and the same reference numerals are given to the parts that are the same as or correspond to those of the first embodiment.

FIG. 9 is a perspective view of the interior of the indoor unit 1 according to Embodiment 2, FIG. 10 is a plan view of the casing according to Embodiment 2 as seen from the suction port side, and FIG. 11 is this embodiment. 2 is a plan view of the inside of the indoor unit 1 according to 2 as seen from the rear side.

As shown in FIG. 9 , the indoor unit 1 according to Embodiment 2 has a guide plate 16 provided to face the heat exchanger 3 . For example, as shown in FIG. 10, the guide plate 16 has a V-shape when viewed from the side of the spiral casing, is downstream of the heat exchangers 3, and is downstream of each of the plurality of heat exchangers 3. is provided on the side surface 13 of the spiral casing so as to connect the ends of the spiral casing. Facing the heat exchanger 3 means that the heat exchanger 3 is installed across the casing suction port 6a from the rotation angle at which the heat exchanger 3 is arranged when viewed in a cross section perpendicular to the rotation axis. It is to arrange the guide plate 16 in an angular range not
In addition, the guide plate 16 is not limited to that shown in FIG. Each downstream end and the end of the guide plate 16 may be separated. Also, the guide plate 16 is not limited to the V-shape, and may be U-shaped or other shapes.

As shown in FIG. 11, when a plurality of centrifugal fans 4 are arranged, the guide plates 16 are provided between adjacent spiral casings and between the spiral casings 6 of the centrifugal fans 4 at both ends and the housing 2. .

When the centrifugal blower 4 is of the double-suction type, the guide plate 16 arranged between adjacent spiral casings has a shape symmetrical about a plane parallel to the side surface 13 of the casing at the midpoint of the adjacent spiral casings. be. The guide plates 16 are slanted from the midpoint between adjacent spiral casings towards the side surfaces 13 of the spiral casings. In FIG. 11, if the vertical direction is the height of the guide plate 16, the height of the guide plate 16 decreases from the middle point between the adjacent spiral casings toward the casing suction port 6a. That is, the height of the guide plate 16 is increased as the distance from the side surface 13 of the spiral casing in the direction in which the rotating shaft 8 extends (horizontal direction in FIG. 11) increases.

Further, when the centrifugal blower 4 is of the single-suction type, the side 13 of the spiral casing of the first centrifugal blower having no suction port and the side 13 of the first centrifugal blower between the adjacent spiral casings. A guide plate 16 is provided so as to connect with the side surface 13 having the suction port among the side surfaces 13 of the spiral casing of the second centrifugal blower adjacent to the second centrifugal fan. The guide plate 16 extends from the side 13 of the spiral casing of the first centrifugal fan that does not have a suction port toward the side 13 that has a suction port of the side 13 of the spiral casing of the second centrifugal fan. It has an inclined shape. Of the plurality of centrifugal fans 4, the guide plates 16 provided between the side surfaces 13 of the centrifugal fans 4 arranged at both ends and the housing 2 also have the same shape. That is, the guide plate 16 inclines from the housing 2 toward the side surface 13 of the spiral casing of the centrifugal fan 4 .

12 is a schematic diagram showing the flow of air in the indoor unit 1 when viewed from the side of the spiral casing, and FIG. 13 is the flow of air in the indoor unit 1 when viewed from the back side of the interior of the indoor unit 1. It is a schematic diagram showing.

When the air flow to the casing suction port 6a of the centrifugal blower 4 is only from the upstream side where the heat exchanger 3 is arranged and is perpendicular to the rotation direction of the impeller, the heat exchanger 3 is After passing through, part of the air does not go to the suction port, but to the bottom surface of the housing 2 on the opposite side where the heat exchanger 3 is arranged, forming vortices at the corners of the bottom surface and reducing pressure loss. and reduce air blow efficiency.

When the guide plate 16 is provided on the side surface 13 of the spiral casing so as to face the heat exchanger 3, as shown in FIG. 16 to the suction port. This eliminates the flow toward the bottom surface of the housing 2 and eliminates the generation of vortices at the corners of the housing.

By arranging an inclined guide plate 16 on the side opposite to where the heat exchanger 3 is arranged in the flow path that passes through the heat exchanger 3 arranged on the upstream side of the centrifugal blower 4 and goes to the casing suction port 6a, the suction It is possible to guide the flow to the mouth, suppress the vortex generated at the corner of the bottom surface of the housing on the opposite side where the heat exchanger 3 is arranged, and reduce the pressure loss in the flow path.

Further, as shown in FIG. 13, when the centrifugal blower 4 is of the double suction type, by arranging the guide plate 16 between the adjacent spiral casings, the airflow directed to the adjacent casing suction port 6a (see FIG. 13) Broken line in the middle) can be rectified, pressure loss due to confluence of flows can be reduced, and air blowing efficiency can be improved. Therefore, it is possible to provide the indoor unit 1 and the air conditioner in which the air blowing efficiency is improved even when the heat exchanger 3 is arranged close to the casing.

As described above, by providing the guide plate 16 on the side surface 13 of the spiral casing so as to face the heat exchanger 3, not only the effect of the first embodiment can be obtained, but also the reduction in pressure loss and the blowing efficiency can be achieved. can be improved.

Embodiment 3.
The indoor unit 1 according to Embodiment 3 of the present disclosure will be described with reference to FIGS. 14 to 17. FIG. The indoor unit 1 according to the third embodiment is obtained by modifying the bell mouth 11 of the indoor unit 1 according to the first embodiment. The description of the configuration that overlaps with that of the first embodiment is omitted, and the same reference numerals are given to the parts that are the same as or correspond to those of the first embodiment.

14 is a perspective view of the interior of the indoor unit 1 according to Embodiment 3, FIG. 15 is a plan view of the spiral casing according to Embodiment 3 as seen from the intake port side, and FIG. 17 is a schematic diagram showing the flow of air taken in by the indoor unit 1 in the cross section of FIG.

As shown in FIG. 15, the indoor unit 1 according to the third embodiment has a bell mouth extending portion 17 extending from the bell mouth 11 of the casing suction port 6a on the side where the heat exchanger 3 is arranged. The bell mouth extending portion 17 is formed so that the boundary line 18 between the bell mouth 11 and the side surface 13 of the spiral casing extends to the side surface 13 in the angle ranges θ ₀ ≤ θ ≤ θ ₁ and θ ₂ ≤ θ ≤ θ ₃ in which the connecting portion 15 is formed. It is formed extending to the side on which the heat exchanger 3 is arranged. That is, in FIG. 15 , the bell mouth 11 extends radially outward of the rotating shaft 8 in the angular ranges θ ₀ ≤ θ ≤ θ ₁ and θ ₂ ≤ θ ≤ θ ₃ where the connecting portion 15 is formed.

As shown in FIG. 16, the diameter of the circular cross section 19 on the upstream side of the bell mouth 11 is larger than the diameter of the circular cross section 20 on the downstream side at the casing suction port 6a. The circular section 19 on the upstream side and the circular section 20 on the downstream side are connected by a smooth curved surface 21 . In the third embodiment, the diameter of the circular cross section 19 on the upstream side of the casing suction port 6a is increased so that the curved surface 21 becomes longer. That is, the bell mouth extending portion 17 is provided by extending the end portion of the bell mouth 11 on the upstream side of the casing suction port 6a toward the side where the heat exchanger 3 is arranged.

As shown in FIG. 17, the air that has passed through the heat exchanger 3 passes through the connecting portion 15 and the bell mouth 11 and is sucked into the impeller 5. The longer the curved surface 21 of the bell mouth 11 is, the more rectified the sucked air is and the smoother the sucked air is by the impeller 5 .

Therefore, in the angle range where the connecting portion 15 of the spiral casing is formed, by providing the bell mouth extending portion 17 that extends the bell mouth 11 toward the heat exchanger side, the heat passing through the heat exchanger 3 and the connecting portion 15 is reduced. The flow is more smoothly sucked into the impeller 5, and the blowing performance is improved.

As described above, in the indoor unit 1 according to Embodiment 3, the bell mouth 11, which is the connecting portion between the casing suction port 6a and the side surface 13, is radially outward of the rotating shaft 8 in the angle range where the connecting portion 15 is formed. By providing the bell mouth extending portion 17 extending toward, not only the effect of the first embodiment can be obtained, but also the pressure loss can be reduced and the ventilation efficiency can be improved.

Although FIG. 15 illustrates an example in which the bell mouth extending portion 17 is divided into two parts, it is not limited to this, and various other shapes can be applied. As another example, a shape in which two bellmouth extending portions are connected may be used, and the same effect as the shape in which the bellmouth is divided into two portions can be obtained.

In the fourth embodiment, in order to lengthen the curved surface 21 of the bell mouth 11, the bell mouth is stretched outward in the radial direction of the rotating shaft 8 so as to increase the diameter of the circular cross section 19 on the upstream side. Although the portion 17 is provided, a configuration in which a projecting portion is provided on the side surface 13 in a direction away from the impeller 5 in the rotation axis direction is also conceivable. However, when air is sucked in from a direction perpendicular to the rotation axis direction of the impeller 5, the suction air collides with the protruding portion protruding from the suction port, causing pressure loss and lowering the blowing efficiency. Therefore, in such a case, it is better to provide the bell mouth extending portion 17 shown in the fourth embodiment.

Embodiment 4.
The indoor unit 1 according to Embodiment 4 of the present disclosure will be described with reference to FIGS. 18 to 20. FIG. The indoor unit 1 according to Embodiment 4 further includes a partition plate 22 in addition to the indoor unit 1 according to Embodiment 1. As shown in FIG. The description of the configuration that overlaps with that of the first embodiment is omitted, and the same reference numerals are given to the parts that are the same as or correspond to those of the first embodiment.

18 is a perspective view of the interior of the indoor unit 1 according to Embodiment 4, FIG. 19 is a plan view of the spiral casing according to Embodiment 4 as viewed from the suction port side, and FIG. FIG. 11 is a schematic diagram showing the flow of air sucked into the indoor unit 1 when viewed from the side of the spiral casing in Mode 4;

As shown in FIG. 18, the indoor unit 1 according to Embodiment 4 extends toward the spiral casing 6 from between one end where the first heat exchanger 3a and the second heat exchanger 3b approach each other. It has a partition plate. Since the partition plate 22 extends toward the spiral casing 6 from between the upper end of the first heat exchanger 3a and the upper end of the second heat exchanger 3b, the first heat exchanger and the second heat exchanger are separated from each other. The space between the two heat exchangers and the spiral casing 6 is partitioned. When a plurality of centrifugal blowers 4 are arranged, a partition plate 22 is provided along the rotating shaft 8 of the centrifugal blower 4 .

As shown in FIG. 19, when viewed from the suction port side of the spiral casing, the partition plate 22 has a front side heat exchanger (first heat exchanger 3a) arranged upstream of the centrifugal fan 4 and a rear side heat exchanger (first heat exchanger 3a). It is a cross-sectional shape that partitions the flow path from the corner side (upper side of the paper surface) formed by the side heat exchanger (second heat exchanger 3b) toward the wall surface 12 of the spiral casing. 19, the partition plate 22 is arranged outside the angle range θ ₁ <θ<θ ₂ where the connecting portion 15 is formed. By providing the partition plate 22 outside the angle range where the connecting portion 15 is formed, it becomes possible to secure a flow path for flowing into the centrifugal fan 4 .

As shown in FIG. 20, when a heat exchanger is arranged on the upstream side of the centrifugal blower 4 so as to surround the spiral casing 6 around the rotation shaft 8, the heat exchanger on the front side (first heat exchange The vessel 3a) and the heat exchanger on the rear side (second heat exchanger 3b) are not arranged parallel but at an angle α. At this time, at a location where the heat exchanger on the front side (first heat exchanger 3a) and the heat exchanger on the back side (second heat exchanger 3b) are close to each other, the respective heat exchange The air that has passed through the unit merges after passing through the heat exchanger, causing pressure loss and possibly reducing blowing efficiency.

Therefore, in the flow path from the heat exchangers 3a, 3b to the casing suction port 6a, the heat exchanger on the front side (first heat exchanger 3a) and the heat exchanger on the back side (second heat exchanger 3b) By arranging the partition plate 22 between, it is possible to prevent the airflow flowing in from the front side and the airflow from the back side from merging, reducing the pressure loss caused by the merging of the flows and improving the ventilation efficiency. can be improved.

In addition, by arranging the partition plate 22, the flow after passing through the heat exchangers 3a and 3b is guided to the connection portion 15 of the spiral casing shown in the first embodiment, and the air blowing efficiency is further improved than that of the first embodiment. can be improved.

As described above, the indoor unit 1 according to Embodiment 4 includes the partition plate 22 extending toward the spiral casing 6 from between the approaching ends of the first heat exchanger 3a and the second heat exchanger 3b. With the provision, not only can the effect of the first embodiment be obtained, but also the pressure loss can be reduced and the blowing efficiency can be improved.

In the fourth embodiment, the case where the heat exchanger 3 is divided into two sheets has been described. The number and shape of the heat exchangers 3 are not limited to those shown in the fourth embodiment.

Embodiment 5.
Air conditioner 30 according to Embodiment 5 of the present disclosure will be described with reference to FIG. 21 . An air conditioner 30 according to the fifth embodiment is an air conditioner including the indoor unit 1 according to the first to fourth embodiments. The description of the configuration that overlaps with that of the first embodiment is omitted, and the same reference numerals are given to the parts that are the same as or correspond to those of the first embodiment.

FIG. 21 is a circuit diagram showing the air conditioner 30 according to the fifth embodiment. The air conditioner 30 is a device that adjusts indoor air, and includes an outdoor unit 31 and an indoor unit 1 as shown in FIG. 21 . The outdoor unit 31 is provided with, for example, a compressor 32, a channel switching device 33, an outdoor heat exchanger 34, an outdoor fan 35, and an expansion section . The indoor unit 1 is provided with, for example, an indoor heat exchanger 37 and an indoor fan 38 . The heat exchanger 3 in Embodiments 1 to 4 corresponds to the indoor heat exchanger 37 , and the centrifugal fan 4 in Embodiments 1 to 4 corresponds to the indoor fan 38 .

The compressor 32, the flow switching device 33, the outdoor heat exchanger 34, the expansion section 36, and the indoor heat exchanger 37 are connected by refrigerant pipes 39 to form a refrigerant circuit. The compressor 32 sucks in a low-temperature, low-pressure refrigerant, compresses the sucked-in refrigerant, converts it into a high-temperature, high-pressure refrigerant, and discharges it. The channel switching device 33 switches the direction in which the refrigerant flows in the refrigerant circuit, and is, for example, a four-way valve. The outdoor heat exchanger 34 exchanges heat, for example, between outdoor air and refrigerant. The outdoor heat exchanger 34 acts as a condenser during cooling operation and acts as an evaporator during heating operation. The outdoor fan 35 is a device that sends outdoor air to the outdoor heat exchanger 34 .

The expansion part 36 is a pressure reducing valve or an expansion valve that reduces the pressure of the refrigerant to expand it. The expansion part 36 is, for example, an electronic expansion valve whose opening is adjusted. The indoor heat exchanger 37 exchanges heat, for example, between indoor air and refrigerant. The indoor heat exchanger 37 acts as an evaporator during cooling operation and acts as a condenser during heating operation. The indoor air blower 38 is a device that sends indoor air to the indoor heat exchanger 37 . The coolant may be water or antifreeze.

Next, the operation modes of the air conditioner 30 will be explained. First, the cooling operation will be explained. In the cooling operation, the refrigerant sucked into the compressor 32 is compressed by the compressor 32 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 32 passes through the flow switching device 33 and flows into the outdoor heat exchanger 34 acting as a condenser. It is heat exchanged with outdoor air sent by 35 and condenses and liquefies. The condensed liquid refrigerant flows into the expansion section 36, where it is expanded and decompressed to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. Then, the gas-liquid two-phase refrigerant flows into the indoor heat exchanger 37 acting as an evaporator, where it exchanges heat with the indoor air sent by the indoor blower 38 to evaporate and become gas. do. At this time, the indoor air is cooled, and cooling is performed in the room. The vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow switching device 33 and is sucked into the compressor 32 .

Next, I will explain the heating operation. In the heating operation, the refrigerant sucked into the compressor 32 is compressed by the compressor 32 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 32 passes through the flow path switching device 33 and flows into the indoor heat exchanger 37 acting as a condenser. It is heat exchanged with the room air sent by 38 and condenses and liquefies. At this time, the indoor air is warmed, and heating is performed in the room. The condensed liquid refrigerant flows into the expansion section 36, where it is expanded and decompressed to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. Then, the gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 34 acting as an evaporator, where it is heat-exchanged with the outdoor air sent by the outdoor fan 35 to evaporate and gasify. do. The vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow switching device 33 and is sucked into the compressor 32 .

As described above, by arranging the indoor unit 1 shown in any one of Embodiments 1 to 4 in the air conditioner 30, as the size of the indoor unit 1 is reduced, when the heat exchanger is arranged close to the casing, Also, it is possible to provide an air conditioner capable of improving the air blowing efficiency while ensuring the capacity of the indoor heat exchanger 37 .

It should be noted that appropriate combinations, modifications, and omissions of the embodiments are also included within the scope of the technical ideas shown in the embodiments.

REFERENCE SIGNS LIST 1 indoor unit 2 housing 2a body suction port 2b body outlet 3 heat exchanger 4 centrifugal blower 5 impeller 6 spiral casing 6a casing suction port 6b casing outlet 7 drive motor 8 rotating shaft 9 main plate 10 blades 11 bell mouth 12 wall surface 13 side surface 14 tongue portion 15 connection portion 16 guide plate 17 bell mouth extension portion 22 partition plate 30 air conditioner 31 outdoor unit, Lc: Distance between adjacent spiral casings, L: Distance between _H heat exchanger and wall surface, Hb: Length of impeller in direction of rotation axis, Hc: Length of wall surface in direction of rotation axis.

Claims

a housing having a body inlet and a body outlet;
An impeller provided inside the housing and having a main plate that rotates about a rotation axis and a plurality of blades arranged on the main plate; a wall surface spirally surrounding the impeller; a centrifugal blower having a spiral casing with a side surface having a suction port for sucking in;
a heat exchanger provided inside the housing and having a curved shape as a whole to surround the wall surface;
with
Letting the angle around the rotation axis be the rotation angle θ, the distance between the wall surface and the heat exchanger be the radial distance L H , and the length of the wall surface in the direction of the rotation axis be Hc,
The heat exchanger is arranged so that the radial distance LH varies depending on the rotation angle θ,
The spiral casing has a connecting portion that connects the wall surface and the side surface in a chamfered manner,
The length Hc of the wall surface in the rotation axis direction at the rotation angle θ at which the radial distance LH is short is longer than the length Hc of the wall surface in the rotation axis direction at the rotation angle θ at which the radial distance LH is long. Short indoor unit.
If the relationship in which the radial distance LH changes with respect to the rotation angle θ is expressed as a function LH (θ),
2. The indoor unit according to claim 1, wherein the function LH ([theta]) has two or more minimum values in a range of angles at which the heat exchanger faces the wall surface.
The indoor unit according to claim 2, wherein the length Hc of the wall surface in the rotation axis direction is the minimum at the rotation angle θ at which the function LH (θ) takes the minimum value.
Assuming that the length of the impeller in the direction of the rotation axis is Hb,
The length Hc of the wall surface in the direction of the rotation axis is shorter than the length Hb of the impeller in the direction of the rotation axis at the rotation angle θ at which the connecting portion is provided. indoor unit.
The indoor unit according to any one of claims 1 to 4, wherein the length Hc of the wall surface in the rotation axis direction varies depending on the size of the connecting portion.
the heat exchangers are arranged at an angle to each other such that one end of each of the first heat exchanger and the second heat exchanger approaches and the other end separates;
The indoor unit according to any one of claims 1 to 5, wherein the centrifugal fan is positioned between the other ends of the first heat exchanger and the second heat exchanger. .
7. The indoor unit according to any one of claims 1 to 6, further comprising a guide plate provided on the side surface so as to face the heat exchanger inside the housing.
A bell mouth, which is a connecting portion between the suction port of the spiral casing and the side surface, further includes a bell mouth extending portion extending radially outward of the rotating shaft in the angular range where the connecting portion is formed. The indoor unit according to any one of claims 1 to 7.
7. The indoor unit according to claim 6, further comprising a partition plate extending toward the spiral casing from between adjacent ends of the first heat exchanger and the second heat exchanger.
An air conditioner comprising the indoor unit according to any one of claims 1 to 9 and an outdoor unit.