WO2020152748A1

WO2020152748A1 - Fan blower, indoor unit, and air conditioner

Info

Publication number: WO2020152748A1
Application number: PCT/JP2019/001661
Authority: WO
Inventors: 惇司河野; 拓矢寺本
Original assignee: 三菱電機株式会社
Priority date: 2019-01-21
Filing date: 2019-01-21
Publication date: 2020-07-30
Also published as: EP3916238A1; CN113302401B; EP3916238A4; JPWO2020152748A1; CN113302401A; JP7086229B2

Abstract

A fan blower (100) is provided with: a motor (20) including a rotational shaft (21) and a drive unit (22); and a centrifugal fan (10) including a main wall (11) fixed to the rotational shaft (21), an annular sidewall (13) disposed spaced apart from the main wall (11) in the rotational-shaft extension direction, and a plurality of blades (12) disposed between the main wall (11) and the sidewall (13). The main wall (11) has a diametrically centrally disposed protuberance (16) in the form of a bulge heading toward the sidewall (13) in said extension direction. The protuberance (16) has a convex surface (16a) and a concave surface (16b) where at least part of the drive unit (22) is accommodated. The height (a) of the protuberance (16) along said extension direction is less than half of the span (b) of an outlet (15) along said extension direction. The span (c) of that portion of the drive unit (22) along said extension direction, such portion being disposed inside the concavity (19), is greater than half of the span (d) of the drive unit (22) along said extension direction.

Description

Blower, indoor unit and air conditioner

The present invention relates to a blower, an indoor unit, and an air conditioner.

Blowers equipped with centrifugal fans are known. WO 2006/126408 is provided with a main plate and a shroud (side plates) that are arranged at intervals in the extending direction of the rotating shaft, and a plurality of blades that are arranged between the main plate and the shroud. A blower is disclosed. The central portion in the radial direction of the main plate is provided in a convex shape with respect to the outer peripheral portion when the centrifugal fan is viewed from the suction port. The central portion of the main plate is provided in a concave shape with respect to the outer peripheral portion when the centrifugal fan is viewed from the side opposite to the suction port. A motor for rotating the blower is housed in the concave portion of the central portion. The inner peripheral end of each blade of the centrifugal fan is provided on the convex portion.

International Publication No. 2006/126408

However, the convex portion of the main plate hinders the inflow of air flow from the suction port of the centrifugal fan to the main plate side in the extending direction between the blades. As a result, the pressure on the main plate side in the extending direction is reduced between the blades, so that the airflow is attracted to the main plate side, and the wind velocity distribution in the extending direction between the blades becomes uneven. As a result, the ventilation efficiency is reduced and the noise is increased. This problem becomes more remarkable as the height of the central portion in the extending direction is higher.

On the other hand, when the height of the central portion of the main plate in the extending direction is lowered, the protruding portion of the motor arranged outside the concave portion of the main plate in the extending direction expands, and the blower extends the extending portion. Increase in size.

The main object of the present invention is to provide a blower in which the reduction of the ventilation efficiency, the increase of noise, and the increase in size are suppressed at the same time as compared with the conventional blower.

The blower according to the present invention includes a rotating shaft, a motor including a drive unit that rotates the rotating shaft, a main plate fixed to the rotating shaft, and a main plate that is arranged at a distance from the main plate in the extending direction of the rotating shaft. A centrifugal fan including an annular side plate and a plurality of blades arranged between the main plate and the side plate and rotated by a motor. The centrifugal fan is provided with an air outlet between the radial outer peripheral end of the main plate and the radial outer peripheral end of the side plate. The main plate is arranged at the center in the radial direction and has a convex portion that is convex toward the side plate in the extending direction. The convex portion has a convex surface provided in a convex shape and a concave surface arranged on the opposite side of the convex surface. At least a part of the drive unit is housed in a recess surrounded by the concave surface. The height a of the protrusion in the extending direction is less than half the width b of the outlet in the extending direction. A width c in the extending direction of a portion of the drive portion, which is arranged inside the recess, is wider than a half of a width d in the extending direction of the drive portion.

According to the present invention, it is possible to provide a blower in which the reduction of the ventilation efficiency, the increase of noise, and the increase in size are suppressed at the same time as compared with the conventional blower.

FIG. 3 is a perspective view showing the blower according to the first embodiment. It is sectional drawing along the rotating shaft of the air blower shown by FIG. 5 is a graph showing the relationship between the fan input and the ratio a/b of the blower according to the first embodiment. It is sectional drawing along the rotating shaft of the air blower which concerns on Embodiment 2. It is sectional drawing along the rotating shaft of the air blower which concerns on Embodiment 3. It is sectional drawing along the rotating shaft of the air blower which concerns on Embodiment 4. It is sectional drawing along the rotating shaft of the air blower which concerns on Embodiment 5. It is sectional drawing along the rotating shaft of the air blower and indoor unit which concern on Embodiment 6. It is a figure which shows the air conditioner provided with the air blower which concerns on any of Embodiments 1-6.

An embodiment of the present invention will be described below with reference to the drawings. In the following drawings, the same or corresponding parts will be denoted by the same reference numerals and description thereof will not be repeated.

Embodiment 1.
As shown in FIGS. 1 and 2, blower 100 according to the first embodiment includes centrifugal fan 10 and motor 20. The centrifugal fan 10 includes a main plate 11, a plurality of blades 12, and side plates 13. The motor 20 includes a rotary shaft 21, a drive unit 22, and a support unit 23. Hereinafter, the extending direction of the rotating shaft 21, the radial direction and the circumferential direction with respect to the extending direction are simply referred to as the extending direction, the radial direction, and the circumferential direction.

The centrifugal fan 10 has rotational symmetry of arbitrary order with respect to the rotating shaft 21. The centrifugal fan 10 has a suction port 14 arranged at the center in the radial direction and opened in the extending direction, and a suction port 14 arranged outside the suction port 14 in the radial direction. An outlet 15 is provided that opens in a direction intersecting with the extending direction.

The main plate 11 is fixed to the rotary shaft 21. The side plate 13 is arranged on the side opposite to the motor 20 with respect to the main plate 11 in the extending direction. The main plate 11 has a convex portion 16 which is arranged at the center in the radial direction and which is convex toward the suction port 14 when the main plate 11 is viewed from the side plate 13 side. The convex portion 16 projects toward the side plate 13 side in the extending direction, in other words, the side opposite to the motor 20. The main plate 11 further has, for example, a flat portion 17 which is provided so as to surround the convex portion 16 in the radial direction and extends in the direction perpendicular to the rotation axis. The outer peripheral end 11b is configured as an outer peripheral end of the flat portion 17, for example. The convex portion 16 and the flat portion 17 are integrally provided. The boundary between the convex portion 16 and the flat portion 17 is a connection between the outer peripheral end portion of the convex portion 16 whose end surface is curved in a cross section along the rotation axis 21 and the inner peripheral end portion of the flat portion 17 whose end surface is planar. It is a point.

The convex portion 16 has a top portion arranged at a position farthest from the flat portion 17 in the extending direction and the radial direction, and an outer peripheral end portion as a bottom portion connected to an inner peripheral end portion of the flat portion 17. Have A boss portion 30 fixed to the rotary shaft 21 is attached to the top of the convex portion 16. As a result, the main plate 11 is fixed to the rotary shaft 21 via the boss portion 30.

The flat portion 17 is provided in an annular shape along the circumferential direction. The flat portion 17 has an inner peripheral end portion connected to the outer peripheral end portion of the convex portion 16 and an outer peripheral end portion forming an outer peripheral end portion 11b of the main plate 11.

The convex portion 16 is arranged on the opposite side of the convex surface 16a and the convex surface 16a protruding from the flat portion 17 when the main plate 11 is viewed from the side plate 13 side, and the main plate 11 is opposite to the side plate 13 side. It has a concave surface 16b which is concave with respect to the flat portion 17 when viewed from the side. The convex portion 16 has a concave portion 19 surrounded by the concave surface 16b inside the flat portion 17 when the main plate 11 is viewed from the side opposite to the side plate 13 side.

The convex surface 16a has, for example, a first curved surface 16aa, a second curved surface 16ab, and a conical surface 16ac. The first curved surface 16aa is arranged closer to the suction port 14 side than the conical surface 16ac in the extending direction, and is arranged closer to the inner peripheral side than the conical surface 16ac in the radial direction. The second curved surface 16ab is arranged closer to the air outlet 15 side than the conical surface 16ac in the extending direction, and is arranged further outward than the conical surface 16ac in the radial direction.

The inner peripheral end portion of the first curved surface 16aa in the radial direction is connected to, for example, the boss portion 30. The radial outer peripheral end of the first curved surface 16aa is connected to, for example, the radial inner peripheral end of the conical surface 16ac. The radial outer peripheral end of the conical surface 16ac is connected to, for example, the radial inner peripheral end of the second curved surface 16ab. The outer circumferential inner end of the second curved surface 16ab in the radial direction is connected to the inner circumferential end of the flat portion 17, for example. The boundary between the first curved surface 16aa and the conical surface 16ac is the outer peripheral end of the first curved surface 16aa whose end surface is curved in a cross section along the rotation axis 21, and the inner peripheral end of the conical surface 16ac whose end surface is straight. Connection point. The boundary between the conical surface 16ac and the second curved surface 16ab is the outer peripheral end of the conical surface 16ac whose end surface forms a straight line in the cross section along the rotation axis 21, and the inner peripheral end of the second curved surface 16ab whose end surface forms a curve. Connection point.

The first curved surface 16aa is provided in a convex shape when the main plate 11 is viewed from the side plate 13 side. The second curved surface 16ab is provided in a concave shape when the main plate 11 is viewed from the side plate 13 side. The conical surface 16ac is a conical surface centered on the rotation axis 21. The center of curvature of the first curved surface 16aa is arranged on the concave surface 16b side with respect to the main plate 11. In other words, the center of curvature of the first curved surface 16aa is arranged on the opposite side of the suction port 14 from the first curved surface 16aa in the extending direction. The center of curvature of the second curved surface 16ab is arranged on the convex surface 16a side with respect to the main plate 11. In other words, the center of curvature of the second curved surface 16ab is arranged closer to the suction port 14 side than the second curved surface 16ab in the radial direction.

Each of the plurality of wings 12 is arranged between the main plate 11 and the side plate 13. Each blade 12 connects, for example, the flat portion 17 of the main plate 11 and the side plate 13. The blades 12 are arranged at intervals in the circumferential direction. The inner peripheral end of each blade 12 is arranged on the outer peripheral side of the outer peripheral end of the convex portion 16, for example.

The side plate 13 is annularly provided along the circumferential direction. The side plate 13 is provided with an inner peripheral end portion 13 a provided so as to form a suction port 14 with the centrifugal fan 10 and an outer peripheral end portion 13 b provided so as to form an outlet port 15 between the main plate 11. And have. The inner peripheral end portion 13a is arranged at a position farther from the flat portion 17 of the main plate 11 than the outer peripheral end portion 13b in the extending direction. In the cross section along the rotation axis 21, the side plate 13 has a curved shape with the center of curvature arranged on the outer peripheral side of the side plate 13 in the radial direction. Each blade 12 is connected, for example, from a portion located on the flat portion 17 side of the inner peripheral end portion 13a of the side plate 13 to an outer peripheral end portion 13b of the side plate 13. The inner peripheral end of each blade 12 is arranged on the inner peripheral side of the inner peripheral end 13a of the side plate 13, for example.

The suction port 14 is configured as an opening surrounded by the inner peripheral end 13a of the side plate 13. When the centrifugal fan 10 is viewed from the extending direction, the suction port 14 has a planar shape of a circle centered on the rotation shaft 21. The centrifugal fan 10 has a plurality of outlets 15 arranged side by side in the circumferential direction. Each of the outlets 15 is arranged between the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 in the extending direction, and is arranged between two blades 12 adjacent to each other in the peripheral direction. ..

As described above, the rotary shaft 21 of the motor 20 is fixed to the main plate 11 of the centrifugal fan 10 via the boss portion 30. The drive unit 22 houses a stator and a rotor that rotates together with the rotating shaft 21 with respect to the stator. The drive portion 22 has a portion housed in the concave portion 19 surrounded by the concave surface 16b of the main plate 11. The drive unit 22 has, for example, a first portion 22a housed in the recess and a second portion 22b arranged outside the recess. The first portion 22a and the second portion 22b are arranged side by side in the extending direction.

The support portion 23 is arranged outside the drive portion 22 in the radial direction, and is fixed to at least one of the first portion 22a and the second portion 22b of the drive portion 22. The support portion 23 has, for example, a portion housed in the recess and a portion arranged outside the recess. The support portion 23 is fixed to the casing of the blower 100 (not shown) by a fixing member (not shown). A heat exchanger (not shown) is fixed to the housing, for example. The heat exchanger is arranged so as to face the air outlet 15 in the radial direction.

As shown in FIG. 2, the maximum distance in the extending direction between the top and the bottom of the convex surface 16a of the convex portion 16 is referred to as the height a of the convex portion 16 with respect to the flat portion 17 of the main plate 11. The longest distance in the extending direction between the outer peripheral end 11b of the flat portion 17 of the main plate 11 and the outer peripheral end 13b of the side plate 13 is equal to the width b of the outlet 15 in the extending direction. The ratio a/b of the height a to the width b is less than 1/2. Preferably, the ratio a/b is less than 1/3. The width b of the blowout port 15 in the extending direction is, for example, equal to or less than the width of the heat exchanger in the extending direction that is arranged so as to face the blowout port 15 in the radial direction.

As shown in FIG. 2, the width c in the extending direction of the first portion 22a disposed inside the recess 19 of the drive unit 22 is less than half the width d in the extending direction of the drive unit 22. Is also wide. In other words, the width c is greater than the width m of the second portion 22b of the drive portion 22 arranged outside the recess 19 in the extending direction (that is, the difference between the width d and the width c). wide. The width m may be zero. In other words, the entire drive unit 22 may be arranged inside the recess 19. In this case, the width c is the width of the entire drive unit 22 in the extending direction, and is larger than zero.

As shown in FIG. 2, the longest distance between the inner peripheral end portions 13a of the side plates 13 arranged to face each other in the radial direction is called the inner diameter e of the suction port 14. The longest distance between the outer peripheral ends of the convex portions 16 arranged so as to sandwich the rotary shaft 21 in the radial direction is referred to as the width f of the convex portions 16. The inner diameter e of the suction port 14 is larger than the width f of the convex portion 16, for example. The height a of the protrusion 16 is, for example, not less than half the width f of the protrusion 16 and not more than the width f. The width b is less than the inner diameter e.

The use of the blower 100 is not particularly limited, but is suitable for, for example, a blower that is placed in an indoor unit of an air conditioner and blows air to an indoor heat exchanger. In this case, the heat exchanger is arranged, for example, at a position facing the air outlet 15 in the radial direction (see FIG. 8).

<Effect>
The blower 100 is arranged with a motor 20 including a rotary shaft 21 and a drive unit 22 for rotating the rotary shaft 21, a main plate 11 fixed to the rotary shaft 21, and a main plate 11 spaced apart in the extending direction. The centrifugal fan 10 includes an annular side plate 13 and a plurality of blades 12 arranged between the main plate 11 and the side plate 13 and is rotated by a motor 20. An opening forming a suction port 14 of the centrifugal fan 10 is provided at the center of the side plate 13 in the radial direction. The main plate 11 has a convex portion 16 which is arranged at the center in the radial direction and which is convex toward the suction port 14 in the extending direction when the main plate 11 is viewed from the side plate 13 side. An air outlet 15 of the centrifugal fan 10 is provided between the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13. The convex portion 16 has a convex surface 16a provided in a convex shape when the main plate 11 is viewed from the side plate 13 side, and a concave surface 16b arranged on the opposite side of the convex surface 16a. At least a part of the drive unit 22 is housed in the recess 19 surrounded by the concave surface 16b. The height a of the convex portion 16 in the extending direction is less than half the width b of the blowout port 15 in the extending direction. The width c in the extending direction of the portion of the drive portion 22 arranged inside the recess 19 is wider than half the width d of the drive portion 22 in the extending direction.

When the ratio a/b is 1/2 or more, the air volume on the side of the main plate 11 in the extending direction between the plurality of blades 12 is reduced, and the gas flowing into the outer peripheral side of the suction port 14 is along the side plate 13. It becomes difficult to flow. Therefore, the wind speed distribution between the blades 12 becomes uneven, and the ventilation resistance between the blades 12 increases. FIG. 3 is a graph showing the relationship between the ratio a/b and the electric power (hereinafter, fan input) supplied to the blower so that the amount of air blown from the blower becomes a set air volume. The horizontal axis of FIG. 3 indicates the ratio a/b, and the vertical axis of FIG. 3 indicates the standardized fan input. As shown in FIG. 3, when the ratio a/b is 1/2 or more, the fan input is increased and the ventilation efficiency is higher than when the ratio a/b is less than 1/2. descend. In this case, the noise of the blower also increases.

Further, if the ratio a/b is set to less than 1/2 by reducing the height a, the width m becomes larger than the width c, and the blower 100 becomes larger in the extending direction. Further, even if the ratio a/b is less than 1/2 by increasing the width b, the blower 100 becomes large in the extending direction.

On the other hand, in the blower 100, the ratio a/b is less than 1/2 and the width c is wider than half the width d. Therefore, as shown in FIG. 3, in the blower 100, compared with the case where the ratio a/b is 1/2 or more, the fan input is reduced, the blowing efficiency is improved, and the noise is reduced. ..

Furthermore, since the width m is narrower than the width c, the blower 100 is prevented from becoming large in the extending direction. Since the convex portion 16 and the motor 20 have a flat shape, the blower 100 in which the ratio a/b is less than 1/2 and the width c is wider than half the width d is realized. The flattening of the motor 20 is realized, for example, by arranging the support portion 23 of the motor 20 outside the drive portion 22 in the radial direction as compared with the motor fixed to the blower without depending on the support portion 23. To be done. For these reasons, in the blower 100, lowering of blowing efficiency, increase of noise, and increase in size are simultaneously suppressed.

Preferably, the ratio a/b is less than 1/3. By doing so, compared with the case where the ratio a/b is 1/3 or more and less than 1/2, the wind speed distribution in the extending direction between the blades 12 becomes more uniform, and the ventilation resistance between the blades 12 is reduced. Then, the fan input is further reduced.

Embodiment 2.
As shown in FIG. 4, the blower 101 according to the second embodiment has basically the same configuration as the blower 100 according to the first embodiment, but the height a of the convex portion 16 is a convex portion. It is different in that it is less than half of the width f of 16.

The longest distance in the extending direction between the top and the bottom of the concave surface 16b of the convex portion 16 is less than half the width f of the convex portion 16. The inner diameter e of the suction port 14 is larger than the width f of the convex portion 16.

When the blower 100 in which the height a of the convex portion 16 is at least half the width f of the convex portion 16 and the blower 100 and the blower 101 having the same inner diameter e are compared, the convex portion 16 of the blower 101 is It is flatter than the convex portion 16 of the blower 100.

In the blower 101, since the height a is less than half of the width f of the convex portion 16, the height of the convex portion 16 is larger than that of the case where the height a is half or more of the width f of the convex portion 16. It is provided flat. Therefore, in the blower 101, the volume of the concave portion 19 of the blower 101 is increased while the height a is reduced as compared with the case where the height a is half or more of the width f of the convex portion 16. There is. As a result, in the blower 101, as compared with the case where the height a of the blower 100 is more than half the width f of the convex portion 16, the reduction of the blowing efficiency, the increase of noise, and the increase in size are further suppressed. ..

Embodiment 3.
As shown in FIG. 5, the blower 102 according to the third embodiment has basically the same configuration as the blower 100 according to the first embodiment, but the width h in the radial direction of the first curved surface 16aa is the above. The difference is that it is wider than the radial width i of the second curved surface 16ab. Note that the blower 102 may have the same configuration as the blower 101 as long as the radial width h of the first curved surface 16aa is wider than the radial width i of the second curved surface 16ab.

The radius of curvature of the first curved surface 16aa is larger than the radius of curvature of the second curved surface 16ab. The width h of the first curved surface 16aa is smaller than the radial width j of the conical surface 16ac, for example. The sum of the width h of the first curved surface 16aa, the width i of the second curved surface 16ab, and the width j of the conical surface 16ac and the radial width of the boss portion 30 is the convex portion. It is equal to the above width f of 16.

In the blower 102, since the width h is wider than the width i, the gas flowing from the suction port 14 to the vicinity of the top of the convex portion 16 smoothly flows along the first curved surface 16aa and the conical surface 16ac. As a result, air flow is less likely to be separated on the first curved surface 16aa and the conical surface 16ac. Further, the gas flowing along the conical surface 16ac is turned along the second curved surface 16ab and flows into the main plate 11 side between the blades 12 in the extending direction. As a result, as compared with the case where the width h is narrower than the width i, the air volume on the side of the main plate 11 in the extending direction is increased, the wind speed distribution between the blades 12 becomes uniform, and the ventilation resistance between the blades 12 is reduced. Decrease. As a result, in the blower 102, the blowing efficiency is further improved and the noise is further reduced, as compared with the case where the width h is smaller than the width i in the blower 100.

Further, when the width h of the first curved surface 16aa is narrower than the radial width j of the conical surface 16ac, even when the airflow is separated on the first curved surface 16aa, the separated airflow is conical. So-called redeposition tends to occur along the surface 16ac. Therefore, the blowing efficiency of the blower 102 in which the width h is narrower than the width j is higher than that of the blower 102 in which the width h is not narrower than the width j.

Fourth Embodiment
As shown in FIG. 6, the blower 103 according to the fourth embodiment has basically the same configuration as the blower 100 according to the first embodiment, but the outer peripheral end 11b of the main plate 11 and the outer peripheral ends of the side plates 13 are the same. The difference is that the portion 13b is curved toward the side opposite to the suction port 14 in the extending direction. Note that the blower 103 is provided with the blower 101 or the blower 102 as long as the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 are curved toward the side opposite to the suction port 14 in the extending direction. You may have the same structure.

The main plate 11 has, for example, a convex portion 16, a flat portion 17, and a first curved portion 18 that is curved with respect to the flat portion 17 toward the side opposite to the suction port 14. The inner peripheral end of the flat portion 17 is connected to the outer peripheral end of the convex portion 16. The radial outer peripheral end of the flat portion 17 is connected to the radial inner peripheral end of the first curved portion 18. The radial outer peripheral end of the first curved portion 18 forms the outer peripheral end 11 b of the main plate 11. In the cross section along the rotation axis 21, the center of curvature of the first bending portion 18 is arranged on the inner circumferential side of the outer circumferential end portion 11b in the radial direction.

The side plate 13 has, for example, a second curved portion 24 having an inner peripheral end portion 13a of the side plate 13 and a third curved portion 25 having an outer peripheral end portion 13b of the side plate 13. In the cross section along the rotation axis 21, the center of curvature of the second curved portion 24 is arranged on the outer peripheral side of the inner peripheral end portion 13a of the side plate 13 in the radial direction. In the cross section along the rotation axis 21, the center of curvature of the third curved portion 25 is arranged on the inner peripheral side of the outer peripheral end portion 13b of the side plate 13 in the radial direction.

The inner peripheral ends of the plurality of blades 12 are arranged between the flat portion 17 of the main plate 11 and the second curved portion 24 of the side plate 13. The outer peripheral ends of the plurality of blades 12 are arranged between the outer peripheral end 11 b of the main plate 11 and the outer peripheral end 13 b of the side plate 13. That is, a part of the plurality of blades 12 located on the blowout port 15 side is arranged between the first bending portion 18 and the third bending portion 25. The interval in the extending direction between the first bending portion 18 and the third bending portion 25 is, for example, constant.

In the blower 103, since the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 are curved toward the opposite side of the suction port 14 in the extending direction, the blower 103 sucks in the extending direction. The gas can be smoothly blown out toward the side opposite to the mouth 14. Therefore, the blower 103 is suitable for a unit that requires the air passage AF along the extending direction on the downstream side of the blower. In the air passage that is formed on the downstream side of the blower 103 and extends along the extending direction, the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 are on the opposite side of the suction port 14 in the extending direction. The bias of the air flow is reduced and the pressure loss is reduced, compared to that of a blower that is not curved toward it. As a result, when the blower 103 is used in the unit, the blower efficiency is as follows when the outer peripheral end 11b and the outer peripheral end 13b are not curved toward the side opposite to the suction port 14 in the extending direction. Higher than the ventilation efficiency when used in the unit.

Embodiment 5.
As shown in FIG. 7, the blower 104 according to the fifth embodiment has basically the same configuration as the blower 100 according to the first embodiment, but is different from the centrifugal fan 10 in the cross section along the rotation axis 21. The first region R1 in which the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 gradually decreases from the suction port 14 toward the outlet port 15, and the outlet port 15 more than the first region R1. A second region R2 that is arranged on the side and in which the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 gradually increases from the suction port 14 toward the outlet port 15 is provided. The difference is. In the blower 104, as in the blower 101, the height a of the convex portion 16 is less than half the width f of the convex portion 16.

In the side plate 13, the first region R1 is located, for example, at a portion located closer to the inner peripheral end 13a side than the connection portion with the inner peripheral end portions of the plurality of blades 12 and closer to the outer peripheral end portion 13b than the connection portion. It is formed between the part to be formed.

The first region R1 is, for example, a first straight line that is perpendicular to a portion of the side plate 13 that is located on the suction port 14 side with respect to the connection portion with the inner peripheral end portions of the blades 12, and the side plate 13 is blown with respect to the connection portion. It is formed between a second straight line perpendicular to the portion located on the outlet 15 side. The distance k between the main plate 11 and the side plate 13 on the first straight line is longer than the distance l between the main plate 11 and the side plate 13 on the second straight line. In the first region R1, the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 is the distance 1 or more and the distance k or less, and gradually increases from the suction port 14 toward the outlet port 15. Decrease to.

The second region R2 is arranged closer to the outlet port 15 side than the first region R1. The second region R2 is provided so as to be continuous with the first region R1. The second region R2 is formed between the outer peripheral end 13b and a portion of the side plate 13 that is located closer to the outer peripheral end 13b than the connecting portion with the inner peripheral end of the plurality of blades 12, for example.

The second region R2 is formed, for example, between the second straight line and the third straight line perpendicular to the outer peripheral end 13b of the side plate 13. The distance 1 between the main plate 11 and the side plate 13 on the second straight line is shorter than the distance between the main plate 11 and the side plate 13 on the third straight line. The distance between the main plate 11 and the side plate 13 on the third straight line is equal to the width b, for example. In the second region R2, the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 is equal to or more than the distance 1 and equal to or less than the distance b, and gradually increases from the suction port 14 toward the air outlet 15. Increase to.

A part of the plurality of blades 12 located on the suction port 14 side is arranged in the region located on the blowout port 15 side in the first region R1. The remaining portions of the plurality of blades 12 located on the side of the air outlet 15 are arranged in the second region R2.

The gas flowing into the centrifugal fan 10 from the suction port 14 in the blower 104 sequentially flows through the first region R1 and the second region R2 and reaches the outlet 15. In other words, the gas flowing in from the suction port 14 flows between the blades 12 after flowing in the region located on the suction port 14 side in the first region R1. In the first region R1, the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 gradually decreases from the suction port 14 toward the outlet port 15, so that the gas flowing between the blades 12 is It is stable, and air flow is less likely to separate near the inner peripheral end of the blade 12. Furthermore, in the second region R2, the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 gradually increases from the suction port 14 toward the outlet port 15, so that the inside of the second region R2 is The flowing gas is boosted by the diffuser effect. As a result, the blowing efficiency of the blower 104 is further increased as compared with that of the blower 100.

Further, in the blower 104, since the height a is less than half of the width b as in the blower 100, the wind speed distribution between the main plate 11 and the side plate 13 at the outlet 15 is made uniform. Therefore, even in the second region R2 in which the diffuser effect is exhibited, the separation of the airflow on the side plate 13 is unlikely to occur. Therefore, the blowing efficiency of the blower 104 is higher than that of the blower in which the centrifugal fan has only a diffuser shape.

Sixth Embodiment
As shown in FIG. 8, the blower 105 according to the sixth embodiment has basically the same configuration as the blower 100 according to the first embodiment, but the width b is the same as that of the blower outlet 15 in the radial direction. The difference is that the width is at least half of the width n in the extending direction of the heat exchangers 40 arranged so as to face each other. The blower 105 may have the same configuration as any one of the blowers 101 to 104 as long as the width b is equal to or more than half the width n.

The blower 105 is provided in the indoor unit 200. The indoor unit 200 includes a blower 105, a heat exchanger 40, and a housing 50. The indoor unit 200 is, for example, a ceiling-embedded indoor unit. The extending direction of the blower 105 is along the vertical direction, and the radial direction is along the horizontal direction. The suction port 14 is open downward.

The heat exchanger 40 is arranged so as to face the outlet 15 in the radial direction of the blower 105.

The housing 50 houses the blower 105 and the heat exchanger 40 inside. The support portion 23 of the blower 105 is fixed to the housing 50 by the fixing member 31. The housing 50 is provided with an opening below the suction port 14 of the blower 105 for taking in indoor air into the suction port 14. A grill 51 is attached to the opening. A plurality of outlets 52 are provided outside the grill 51 in the radial direction to blow out the air blown from the blower outlet 15 of the blower 105 and heat-exchanged with the refrigerant in the heat exchanger 40 into the room. .. The heat exchanger 40 is arranged inside the housing 50 between the blower outlet 15 and the blower outlet 52 of the blower 105. The upper end of the heat exchanger 40 is connected to the housing 50. The lower end of the heat exchanger 40 is connected to the drain pan 53.

The width b of the blower 105 is more than half the width n in the extending direction of the heat exchanger 40 arranged so as to face the outlet 15 in the radial direction. The width b is less than or equal to the width n. The outer peripheral end 11b of the main plate 11 of the blower 105 is arranged, for example, above the central portion of the heat exchanger 40 in the extending direction. The outer peripheral end portion 13b of the side plate 13 of the blower 105 is arranged, for example, below the central portion of the heat exchanger 40 in the extending direction.

In the extending direction, the outer peripheral end 13b of the side plate 13 is arranged closer to the center of the heat exchanger 40 than the drain pan 53.

Like the blower 100, the blower 105 has the height a less than half of the width b, so that the wind velocity distribution between the main plate 11 and the side plate 13 at the outlet 15 is made uniform. Therefore, even if the width b is relatively wide, that is, half or more of the width n of the heat exchanger 40, separation of the air flow on the side plate 13 is unlikely to occur.

In the blower 105, the difference between the width b and the width n is smaller than in the case where the width b of the outlet 15 is less than half the width n of the heat exchanger. Therefore, the wind speed in the heat exchanger 40 is small. The distribution is made uniform and the pressure loss of gas is reduced.

Further, in the blower 105, the outer peripheral end 13b of the side plate 13 is arranged closer to the center of the heat exchanger 40 than the drain pan 53 in the extending direction. Therefore, in the indoor unit 200 including the blower 105, the gas blown out from the blowout port 15 is less likely to collide with the drain pan 53, so that an increase in ventilation resistance in the indoor unit 200 is suppressed.

The indoor unit 200 equipped with the blower 105 has a lower ventilation efficiency, an increased noise, and a larger size at the same time than the indoor unit equipped with the conventional blower.

As shown in FIG. 9, blowers 100 to 105 according to Embodiments 1 to 6 can be applied to air conditioner 300. The air conditioner 300 includes, for example, an indoor unit 200 and an outdoor unit 210. The indoor unit 200 includes a heat exchanger 40 and blowers 100 to 105. The outdoor unit 210 includes a compressor 211, an outdoor heat exchanger 212, an expansion valve 213, a four-way valve 214, and an outdoor blower 215. The indoor unit 200 and the outdoor unit 210 are connected to each other via a plurality of refrigerant pipes, and the indoor unit 200, the outdoor unit 210, and the plurality of refrigerant pipes include a compressor 211, an outdoor heat exchanger 212, an expansion valve 213, A refrigerant circuit including the four-way valve 214 and the heat exchanger 40 is configured. From a different point of view, the air conditioner 300 includes at least one blower 100 to 105, an air passage provided on the downstream side of the air outlet 15 of the at least one air blower 100 to 105, and an air passage in the air passage. And the heat exchanger 40 arranged. In the air conditioner 300, the blowers 100 to 105 are used as, for example, blowers for blowing air to the indoor heat exchanger in an indoor unit. The indoor unit 200 including the

blowers

100, 101, 103 to 105 has the same configuration as the indoor unit 200 shown in FIG. 8, for example. In the indoor unit 200 including the blower 102, for example, an air passage provided on the downstream side of the blowout port 15 extends toward the opposite side of the suction port 14 in the extending direction from the blowout port 15, and A heat exchanger 40 is arranged in the air passage.

The embodiments of the present invention have been described above, but the above-described embodiments can be modified in various ways. Further, the scope of the present invention is not limited to the above embodiment. The scope of the present invention is shown by the claims, and is intended to include meanings equivalent to the claims and all modifications within the scope.

10 centrifugal fan, 11 main plate, 11b, 13b outer peripheral end, 12 blades, 13 side plate, 13a inner peripheral end, 14 inlet, 15,52 outlet, 16 convex, 16a convex, 16aa first curved surface, 16ab first 2 curved surfaces, 16b concave surface, 17 flat portion, 18 first curved portion, 19 concave portion, 20 motor, 21 rotary shaft, 22 drive portion, 22a first portion, 22b second portion, 23 support portion, 24 second curved portion, 25 third curved portion, 30 boss portion, 31 fixing member, 40 heat exchanger, 50 housing, 51 grill, 53 drain pan, 100, 101, 102, 103, 104, 105 blower, 200 indoor unit, 300 air conditioner ..

Claims

A motor including a rotating shaft and a drive unit that rotates the rotating shaft;
A main plate fixed to the rotating shaft, an annular side plate arranged at a distance from the main plate in the extending direction of the rotating shaft, and a plurality of arranged between the main plate and the side plate. A centrifugal fan including a blade and rotated by the motor,
The centrifugal fan is provided with an outlet between an outer peripheral end of the main plate in a radial direction with respect to the rotation axis and an outer peripheral end of the side plate in the radial direction,
The main plate has a convex portion that is arranged at the center in the radial direction and is convex toward the side plate side in the extending direction,
The convex portion has a convex surface provided in a convex shape, and, and has a concave surface arranged on the opposite side to the convex surface,
At least a part of the drive unit is arranged inside a recess surrounded by the concave surface,
The height a of the convex portion in the extending direction is less than half the width b of the outlet in the extending direction,
The blower in which the width c in the extending direction of the at least a portion of the drive unit disposed inside the recess is larger than half the width d in the extending direction of the drive unit.
The centrifugal fan is provided with a suction port surrounded by an inner peripheral end portion of the side plate in a radial direction with respect to the rotating shaft,
The inner diameter e of the suction port is larger than the radial width f of the convex portion,
The height a is less than half the width f,
The blower according to claim 1, wherein the plurality of blades have an inner peripheral end portion that is arranged outside the convex portion in the radial direction.
The centrifugal fan is provided with a suction port surrounded by an inner peripheral end portion of the side plate in a radial direction with respect to the rotating shaft,
In a cross section along the rotation axis, the convex surface of the convex portion is a conical surface having the rotation axis as a center, a first curved surface arranged closer to the suction port than the conical surface, and the conical surface. A second curved surface that is arranged closer to the outlet than
When the main plate is viewed from the side plate side, the first curved surface is provided in a convex shape and the second curved surface is provided in a concave shape,
The blower according to claim 1 or 2, wherein the radial width h of the first curved surface is wider than the radial width i of the second curved surface.
4. The outer peripheral end of the main plate and the outer peripheral end of the side plate are curved toward the side opposite to the outlet in the extending direction, according to any one of claims 1 to 3. Blower.
The centrifugal fan is provided with a suction port surrounded by an inner peripheral end portion of the side plate in a radial direction with respect to the rotating shaft,
In a cross section along the rotation axis, in the centrifugal fan, the distance between the main plate and the side plate on a straight line perpendicular to the side plate gradually decreases from the suction port toward the outlet port. And a distance between the main plate and the side plate on a straight line that is disposed on the side of the first region and on the outlet side with respect to the first region, and that extends from the suction port toward the outlet port. The blower according to any one of claims 1 to 3, further comprising a second region that gradually increases.
A blower according to any one of claims 1 to 5,
A heat exchanger arranged to face the outlet in the radial direction,
The indoor unit in which the width b is at least half the width n of the heat exchanger in the extending direction.
Further comprising a drain pan connected to one end of the heat exchanger in the extending direction,
The indoor unit according to claim 6, wherein, in the extending direction, the outer peripheral end portion of the side plate is arranged at a position closer to the center of the heat exchanger than the drain pan.
A blower according to any one of claims 1 to 5,
An air conditioner, comprising: a heat exchanger arranged in an air passage downstream of the air outlet of the blower.