WO2022201468A1

WO2022201468A1 - Blower device

Info

Publication number: WO2022201468A1
Application number: PCT/JP2021/012710
Authority: WO
Inventors: 誠田中; 嘉浩小見山; 成浩岡田
Original assignee: 東芝キヤリア株式会社
Priority date: 2021-03-25
Filing date: 2021-03-25
Publication date: 2022-09-29
Also published as: JPWO2022201468A1; JP7458552B2; CN116601392A

Abstract

Provided is a blower device which efficiently takes in air from a bell mouth and can blow air with high efficiency. A blower device (6) comprises an annular bell mouth (7); a downstream-side surface (19) which is flat and continuous with the downstream-side end (7b) of the bell mouth (7); and an impeller (23) which takes in air from the bell mouth (7) and blows air out in the direction along the downstream-side surface (19). The impeller (23) comprises a main plate part (31) which is substantially parallel to the downstream-side surface (19) and which extends radially, and a plurality of open-type blade parts (32) which protrude from the main plate part (31) toward the downstream-side surface (19) and the bell mouth 7, and which are arranged in an annular manner. The maximum outer diameter drawn by the plurality of blade parts (32) is larger than the maximum outer diameter of the main plate part (31). The protruding ends (32a) of the blade parts (32) each have a first part (45) which is disposed in proximity to the downstream-side surface (19), and a second part (46) which protrudes more toward the upstream-side end (7a) of the bell mouth (7) than the downstream-side end (7b) of the bell mouth 7.

Description

blower

The embodiment of the present invention relates to a blower.

A blower that includes a turbofan and a bell mouth on the suction side of the turbofan is known.

WO2009/054316

Conventional blower turbofans are equipped with shrouds that connect the tips of the blades. This shroud is arranged near the bellmouth.

In addition, the inventors have found that in a conventional air blower in which a turbofan shroud is arranged near the bell mouth, a vortex is generated on the back side of the bell mouth (inside the housing) and in the radially outer region of the shroud. found to occur. This vortex reduces the amount of air drawn by the blower.

Therefore, an object of the present invention is to provide a blower capable of efficiently sucking air from a bell mouth and blowing air with high efficiency.

An air blower according to an embodiment of the present invention includes an annular bell mouth, a flat downstream side surface that continues to the downstream end of the bell mouth, sucks air from the bell mouth, and blows air in a direction along the downstream side. and an impeller. The impeller includes a main plate portion that extends substantially parallel to the downstream side surface and extends radially, and a plurality of open blades that are annularly arranged and protrude from the main plate portion toward the downstream side surface and the bellmouth. and The outermost diameter drawn by the plurality of wing portions is larger than the outermost diameter of the main plate portion. The protruding ends of the plurality of wing portions include a first portion arranged close to the downstream side surface and a second portion protruding toward the upstream end of the bell mouth from the downstream end of the bell mouth. It has a part and a.

Further, in the blower device according to the embodiment, it is preferable that the exit angle of the root portion of each blade portion connected to the main plate portion is larger than the entrance angle of the root portion.

Furthermore, in the blower device according to the embodiment, it is preferable that the root portion of each of the blade portions connected to the main plate portion has a linear shape.

Further, in the blower device according to the embodiment, it is preferable that the thickness of each of the blade portions is thinner than the thickness of the main plate portion.

Furthermore, in the air blower according to the embodiment, it is preferable that the number of the plurality of blade portions is a prime number. A first line segment connecting the trailing edge of the first blade portion and the rotation center line, and the trailing edge of the second blade portion adjacent to the first blade portion, when viewed from the direction along the rotation center line of the impeller. and the second line segment connecting the center line of rotation is preferably 25 degrees or more.

Also, in the blower device according to the embodiment, it is preferable to include a reinforcing member that connects the second portions of the plurality of blade portions.

According to the present invention, it is possible to provide a blower capable of efficiently sucking air from the bell mouth and blowing air with high efficiency.

BRIEF DESCRIPTION OF THE DRAWINGS The typical perspective view of the indoor unit of the refrigerating-cycle apparatus provided with the air blower which concerns on embodiment of this invention. BRIEF DESCRIPTION OF THE DRAWINGS The typical longitudinal cross-sectional view of the indoor unit of the refrigerating-cycle apparatus provided with the air blower which concerns on embodiment of this invention. The top view of the impeller which concerns on this embodiment. The perspective view which shows the impeller which concerns on this embodiment from the bottom face side. FIG. 2 is a vertical cross-sectional view of an impeller and a bell mouth according to the present embodiment; The perspective view of the blade part of the impeller which concerns on this embodiment. The figure which compares the characteristic of the impeller which concerns on this embodiment, and the characteristic of the impeller of a comparative example. FIG. 4 is a schematic diagram of the inlet angle and the outlet angle of the blade portion of the impeller according to the present embodiment. The figure which compares the characteristic of the impeller which concerns on this embodiment, and the characteristic of the impeller of a comparative example. The perspective view which shows the other example of the impeller which concerns on this embodiment from the bottom face side. The perspective view which shows the other example of the impeller which concerns on this embodiment from the bottom face side.

An embodiment of a blower device according to the present invention will be described with reference to FIGS. 1 to 11. FIG. In addition, the same code|symbol is attached|subjected to the same or corresponding structure in several drawings.

FIG. 1 is a schematic perspective view of an indoor unit of a refrigeration cycle apparatus equipped with a blower according to an embodiment of the present invention.

Fig. 2 is a schematic vertical cross-sectional view of an indoor unit of a refrigeration cycle apparatus equipped with a blower according to an embodiment of the present invention.

The refrigeration cycle apparatus according to this embodiment includes an indoor unit 1 installed indoors as a user side and an outdoor unit (not shown) installed outdoors as a heat source side, as shown in FIG. .

In addition, the refrigeration cycle device includes a refrigeration cycle (not shown). The refrigeration cycle includes a heat source side heat exchanger (not shown), a compressor (not shown), a heat exchanger 2 on the user side, an expander (not shown), and a refrigerant that circulates the refrigerant through these devices. a tube (not shown); The refrigeration cycle may include a four-way valve (not shown) for switching between cooling operation and heating operation of the refrigeration cycle device.

The indoor unit 1 accommodates a heat exchanger 2 on the user side of the refrigeration cycle. The outdoor unit accommodates a heat source side heat exchanger, a compressor, and a four-way valve of the refrigeration cycle. The expander may be housed in the indoor unit 1 or may be housed in the outdoor unit. The outdoor unit and the indoor unit are connected via a connecting pipe (not shown). The transition pipe is part of the refrigerant pipe. The refrigeration cycle device circulates a refrigerant between a heat exchanger on the outdoor unit side and a heat exchanger 2 on the indoor unit 1 side to harmonize indoor air.

The installation location of the indoor unit 1 is inside the building. The indoor unit 1 is installed by being embedded in the indoor ceiling or suspended from the ceiling or beams.

As shown in FIGS. 1 and 2, the indoor unit 1 according to this embodiment includes a housing 5, a heat exchanger 2 provided inside the housing 5, and a blower 6. The blower device 6 includes an annular bell mouth 7 provided on the housing 5 and a turbo fan 8 that sucks air from the bell mouth 7 and blows the air onto the heat exchanger 2 .

In addition, the indoor unit 1 includes an electric expansion valve (not shown) that is an expander of a refrigeration cycle.

The housing 5 is a box having a rectangular top surface, four rectangular side surfaces, and a rectangular bottom surface. The top surface of the housing 5 is covered with a top plate 11. - 特許庁A turbo fan 8 is provided on the bottom surface of the top plate 11 . Four side surfaces of the housing 5 are covered with side plates 12 . The corners between the sides are beveled like a chamfer. This chamfered portion is closed with an inclined plate 13 .

The bottom surface of the housing 5 is covered with a bottom plate 14. A circular suction port 16 for sucking air from below the indoor unit 1 is provided in the central portion of the bottom plate 14 . A plurality of rectangular outlets 17 for blowing air downward are provided on the outer edge of the bottom plate 14 . Each air outlet 17 extends along each side of the rectangular bottom surface of the housing 5 . Therefore, the indoor unit 1 sucks indoor air from the suction port 16 on the bottom surface of the housing 5, heat-exchanges the refrigerant and the air in the heat exchanger 2, and heats the air from the blowout port 17 on the bottom surface of the housing 5. blow out the air.

The heat exchanger 2 is fixed to the top plate 11 of the housing 5. In this embodiment, the heat exchanger 2 is, for example, of a fin-and-tube type, and includes a large number of aligned aluminum alloy fins and refrigerant pipes passing through the fan.

The heat exchanger 2 is provided inside the housing 5 and surrounds the radially outer side of the turbo fan 8 . The inner peripheral surface of the heat exchanger 2 faces the turbo fan 8 , and the outer peripheral surface of the heat exchanger 2 faces the inner surface of the side plate 12 . The heat exchanger 2 has a flat plate portion 2a facing each side plate 12 of the housing 5 and a curved plate 13 between two adjacent side plates 12 to connect the two adjacent flat plate portions 2a. and a curved plate portion 2b. There are four flat plate portions 2a and three curved plate portions 2b. That is, the heat exchanger 2 is not continuous annular.

An annular bell mouth 7 is provided at the suction port 16 of the bottom plate 14 . The opening edge of the bell mouth 7 on the suction side, that is, the upstream end 7 a of the bell mouth 7 continues to the outer surface 14 a of the bottom plate 14 . The opening edge of the bell mouth 7 on the blowout side, that is, the downstream end 7 b of the bell mouth 7 continues to the inner surface 14 b of the bottom plate 14 . An inner surface 14 b of the bottom plate 14 is flat and reaches the heat exchanger 2 from the downstream end 7 b of the bell mouth 7 . The outer surface 14a of the bottom plate 14 is a flat upstream side surface 18 connected to the upstream end 7a of the bellmouth 7, and the inner surface 14b of the bottom plate 14 is a flat downstream side surface 19 connected to the downstream end 7b of the bellmouth 7. be.

A drain pan (not shown) may be provided below the heat exchanger 2 to receive condensed water generated on the surface of the heat exchanger 2 . During cooling operation in which the heat exchanger 2 functions as an evaporator, the moisture contained in the air passing through the heat exchanger 2, that is, the humidity in the room, condenses on the surface of the heat exchanger 2 and condenses on the heat exchanger 2 as condensed water. It adheres and drips from the heat exchanger 2. A drain pan receives condensed water falling from the heat exchanger 2 . Condensed water stored in the drain pan is pumped up by a drain pump (not shown) provided in the housing 5 and discharged to the outside of the indoor unit 1 through a drain pipe (not shown).

The drain pan preferably has a concave portion for receiving condensed water in a portion where the planar portion extending from the downstream end 7b of the bell mouth 7 to the heat exchanger 2 is as close to the heat exchanger 2 as possible. The drain pan is preferably formed in a heat insulating material integrated with the bottom plate 14 of the housing 5 .

The turbo fan 8 includes a fan motor 22 having a rotating shaft 21 extending in the vertical direction, and an impeller 23 fixed to the rotating shaft 21 so as to rotate integrally.

The fan motor 22 rotates the impeller 23 . The fan motor 22 is fixed to the inner surface of the top plate 11 of the housing 5 via fixtures 25 .

The rotationally driven impeller 23 sucks the air around the housing 5 from the bell mouth 7 of the suction port 16, blows out the air radially in the direction along the inner surface 14b of the bottom plate 14, and directs the blown air to the heat exchanger 2. Spray.

In plan view, the center of the substantially annular heat exchanger 2, the rotation center of the turbo fan 8, the center of the circular suction port 16, and the center of the annular bell mouth 7 are aligned. A maximum outer diameter A of the turbofan 8 is larger than an opening diameter B of the bell mouth 7 .

The rotation center line C of the impeller 23 coincides with the rotation shaft 21 of the fan motor 22 and extends vertically with the indoor unit 1 installed.

When the air conditioner is in cooling operation, the compressor of the outdoor unit discharges high-temperature and high-pressure gas refrigerant and sends it to the heat exchanger (condenser) on the outdoor side. The outdoor-side heat exchanger exchanges heat between the refrigerant flowing therein and the outdoor air to condense the refrigerant. The condensed liquid refrigerant is sent to the indoor unit 1 through the refrigerant pipe. The indoor unit 1 expands the liquid refrigerant flowing from the refrigerant pipe with an electric expansion valve, and sends a low-temperature gas-liquid mixed refrigerant to the heat exchanger 2 (evaporator). The heat exchanger 2 exchanges heat between the low-temperature refrigerant flowing therein and the indoor air to gasify the refrigerant. At this time, the room is cooled by the low-temperature air blown out from the indoor unit 1 .

When the air conditioner is operated for heating, the compressor of the outdoor unit discharges high-temperature and high-pressure gas refrigerant and sends it to the heat exchanger 2 (condenser) of the indoor unit 1. The heat exchanger 2 exchanges heat between the refrigerant flowing inside and the air in the room to condense the refrigerant. At this time, the room is heated by the high-temperature air blown out from the indoor unit 1 .

Next, the impeller 23 will be described in detail.

FIG. 3 is a plan view of the impeller according to this embodiment.

FIG. 4 is a perspective view showing the impeller according to this embodiment from the bottom side.

FIG. 5 is a longitudinal sectional view of the impeller and bell mouth according to this embodiment.

As shown in FIGS. 3 to 5 in addition to FIGS. 1 and 2, the impeller 23 of the blower device 6 according to the present embodiment is substantially parallel to the downstream side 19 connected to the bell mouth 7 and is arranged radially. a plurality of wing portions 32 protruding from the main plate portion 31 toward the downstream side surface 19 and the bell mouth 7 and arranged in an annular shape; and a hub portion 33 provided at the center of the main plate portion 31. I have.

The impeller 23 is an integrally molded product made of fiber reinforced plastic (FRP), aluminum alloy, or magnesium metal. The impeller 23 is made of fiber-reinforced plastic, for example, and integrally molded by hand lay-up.

The main plate portion 31 has a flat plate shape with a substantially uniform thickness. The main plate portion 31 is an assembly of a plurality of petal portions 35 radially extending from the hub portion 33 in the radial direction of the impeller 23 .

Each petal portion 35 has a first side portion 35a having a linear edge and a second side portion 35b having a linear edge. Or it extends in a tapered shape. The first side portion 35 a of each petal portion 35 is also called the first edge of the main plate portion 31 , and the second side portion 35 b of each petal portion 35 is also called the second edge of the main plate portion 31 .

For a pair of adjacent petals 35 , the first side 35 a of one petal 35 faces the second side 35 b of the other petal 35 . In other words, the first side portion 35a of one petal portion 35 and the second side portion 35b of the other petal portion 35 face each other with a gap in the circumferential direction of the main plate portion 31 .

The shapes of all the petals 35 are substantially the same. The ends of the plurality of petals 35 located radially inward of the turbofan 8 , that is, the root ends of the plurality of petals 35 tightly surround the outer periphery of the hub portion 33 . In other words, for a pair of adjacent petals 35 , the root end of the first side portion 35 a of one petal portion 35 coincides with the root end of the second side portion 35 b of the other petal portion 35 . The ends of the plurality of petals 35 located radially outward of the turbofan 8, that is, the projecting ends of the plurality of petals 35, are connected by a virtual circle. This virtual circle corresponds to the outermost diameter D<b>1 of the main plate portion 31 .

A plurality of wing portions 32 and hub portions 33 protrude from the main plate portion 31 in the same direction. The hub portion 33 has a truncated cone shape that tapers away from the main plate portion 31 . The protrusion height of the plurality of blade portions 32 with respect to the main plate portion 31 is higher than the protrusion height of the hub portion 33 .

The number of wings 32, that is, the number of wings is a prime number, and is 11 in this embodiment.

The shape of all wings 32 is substantially the same. All wings 32 are plates of uniform thickness. The plurality of wings 32 are open. That is, the impeller 23 does not have a shroud that connects the projecting ends 32a of the plurality of blades 32. As shown in FIG. Each wing portion 32 is connected only to the main plate portion 31 and is not in contact with and is not connected to the hub portion 33 .

A root end 32 b of each wing portion 32 is an edge of each wing portion 32 that continues to the main plate portion 31 . A root end 32b of each wing portion 32 continues to a first side portion 35a of each petal portion 35 . Each wing portion 32 protrudes from the first side portion 35 a of each petal portion 35 . Therefore, the root end 32b of each wing portion 32 has the same linear shape as the first side portion 35a of each petal portion 35 and has a linear shape that matches the chord of the blade.

Each blade portion 32 is inclined in the circumferential direction of the turbofan 8 and in the direction away from the second side portion 35b of each petal portion 35. Further, each blade portion 32 is inclined radially outward of the turbofan 8 from the root end 32b toward the projecting end 32a. Therefore, the outermost diameter D2 drawn by the plurality of blade portions 32 is larger than the outermost diameter D1 of the main plate portion 31 .

The impeller 23 rotates in a direction R in which the first side portion 35a of each petal portion 35 precedes the second side portion 35b to flow air. That is, the front edge 41 of each blade 32 is positioned on the inner peripheral side of the impeller 23 , and the trailing edge 42 of the blade 32 is positioned on the outer peripheral side of the impeller 23 .

When viewed from the direction along the rotation centerline of the impeller 23 ( FIG. 3 ), a first line segment L1 connecting the trailing edge 42 of the first blade portion 32 and the rotation centerline C and the first line segment L1 adjacent to the first blade portion 32 The angle θ between the trailing edge 42 of the second wing portion 32 and the second line segment L2 connecting the rotation center line C is preferably 25 degrees or more. That is, the number of wings 32 is preferably a prime number of 13 or less, and is 11 in this embodiment.

The protruding end 32a of each wing portion 32 protrudes toward the upstream end 7a of the bell mouth 7 from the first portion 45 arranged close to the downstream side 19 and the downstream end 7b of the bell mouth 7. and a second portion 46 where the second portion 46 is located. That is, the protruding end 32 a of each wing 32 has a convex portion 47 that enters the inside of the bell mouth 7 . The convex portion 47 protrudes following the shape of the bell mouth 7 . The second portion 46 is the ridgeline of the convex portion 47 . In this embodiment, the first portion 45 of the wing portion 32 and the downstream side surface 19 are arranged to face each other with an interval of about several millimeters therebetween. The distance between the impeller 23 and the bell mouth 7 is preferably as close as possible within the range in which the impeller 23 can rotate smoothly without interfering with the bell mouth 7 .

The thickness of each wing portion 32 is thinner than the thickness of the main plate portion 31 . Such a thickness relationship is compared to the case where the thickness of each wing portion 32 is the same as the thickness of the main plate portion 31 or the case where the thickness of each wing portion 32 is thicker than the thickness of the main plate portion 31. , reduce the centrifugal force acting on the wings 32 . The reduction in centrifugal force reduces the deformation of the wing portions 32 and prevents the reduction in the air volume due to the deformation of the wing portions 32 . Further, the main plate portion 31, which is thicker than each wing portion 32, reduces deformation of the wing portions 32 due to centrifugal force, and prevents reduction in air volume due to deformation of the wing portions 32.

FIG. 6 is a perspective view of the wing portion of the impeller according to this embodiment.

As shown in FIG. 6, the planar shape of the blade portion 32 of the impeller 23 according to this embodiment is close to a quadrangle, for example, a parallelogram. The root end 32b has a linear shape that continues to the first side portion 35a of the petal portion 35 . A straight line connecting point a and point b in FIG. 6 is root end 32b. The protruding end 32a has a non-linear shape and has a protrusion 47 that passes through the protruding end of the trailing edge 42 and protrudes in a direction away from the root end 32b with respect to an imaginary line VL parallel to the root end 32b. The projecting end 32a is a line connecting points c, d, and e in FIG.

A line connecting points a and c in FIG. 6 is the leading edge 41 of the wing 32 , and a line connecting points b and e in FIG.

The convex portion 47 has a straight edge 48 that continues to the front edge 41 and is parallel to the root end 32 b and parallel to the main plate portion 31 , and a curved edge 49 that connects the straight edge 48 and the rear edge 42 . . A straight edge 48 is a straight line connecting points c and d in FIG. 6, and a curved edge 49 is a curved line connecting points d and e in FIG. The straight edge 48 and part of the curved edge 49 that follows the bellmouth 7 are the second portion 46 of the protruding end 32a, and the remainder of the curved edge 49 is the first portion 45 located adjacent the downstream side 19. is. That is, the remainder of curvilinear edge 49 is substantially parallel to root end 32b. Between the protruding end 32 a and the bell mouth 7 and between the protruding end 32 a and the downstream side surface 19 , there are gaps that do not hinder the rotation of the impeller 23 . This gap is preferably 5 millimeters or less.

FIG. 7 is a diagram comparing the characteristics of the impeller according to the present embodiment and the characteristics of the impeller of the comparative example.

FIG. 7 is a diagram showing the relationship between the static pressure P of the impeller and the flow rate Q of the impeller, which is the so-called PQ characteristic.

Unlike the impeller 23 according to the present embodiment, the impeller of the comparative example does not have the protrusions 47 on each of the blades 32, and has projecting ends parallel to the downstream side surface 19 and the main plate portion 31. there is The protruding end of the impeller of the comparative example does not protrude into the bell mouth 7 and is arranged close to the downstream side 19 that is arranged on the same plane and continues to the bell mouth 7 .

Also, the PQ characteristic of the impeller 23 according to the present embodiment is represented by a curve α1, and the PQ characteristic of the impeller of the comparative example is represented by a curve γ1.

As shown in FIG. 7, the impeller 23 according to this embodiment can blow more air than the impeller of the comparative example. Further, the impeller 23 according to the present embodiment can obtain a higher static pressure than the impeller of the comparative example by bringing it close to the bellmouth 7 .

FIG. 8 is a schematic diagram of the inlet angle and outlet angle of the blade portion of the impeller according to this embodiment.

The inlet angle and the outlet angle of the blade portion 32 are represented by angles based on the rotation direction of the impeller 23. That is, the inlet angle of the wing portion 32 is the angle between the propelling direction u of the wing portion 32 and the forward direction of the blade arc, and the exit angle of the wing portion 32 is the angle between the propelling direction u of the wing portion 32 and the backward direction of the blade arc. is the angle formed by

As shown in FIG. 8, the blade portion 32 of the impeller 23 according to the present embodiment has an inlet angle β1 of the root end 32b, an outlet angle β2 of the root end 32b, an inlet angle β3 of the projecting end 32a, and an angle β3 of the projecting end 32a. It has an exit angle β4.

The exit angle β2 of the root end 32b is greater than the entrance angle β1 of the root end 32b.

The entrance angle β3 of the protruding end 32a and the exit angle β4 of the protruding end 32a may be appropriately set from the respective velocity triangles. The protruding end 32 a has a curved shape that protrudes outward in the radial direction of the impeller 23 .

The airfoil of the wing portion 32 is a three-dimensional shape that smoothly continues from the linear root end 32b to the curved protruding end 32a. Therefore, the airfoil of each airfoil portion 32 is a plate of substantially uniform thickness that is convexly curved radially outwardly of the impeller 23 so that the protruding distance from the chord increases as it approaches the protruding end 32a. Shape.

FIG. 9 is a diagram comparing the characteristics of the impeller according to the present embodiment and the characteristics of the impeller of the comparative example.

FIG. 9 is a diagram showing the relationship between the static pressure P of the impeller and the flow rate Q of the impeller, which is the so-called PQ characteristic.

Unlike the impeller 23 according to the present embodiment, the outlet angle β2 of the root end 32b of the impeller of the comparative example is smaller than the inlet angle β1 of the root end 32b. A curve α2 represents the PQ characteristic of the impeller 23 according to the present embodiment, and a curve γ2 represents the PQ characteristic of the impeller of the comparative example.

As shown in FIG. 9, the impeller 23 according to this embodiment can blow more air than the impeller of the comparative example. Further, the impeller 23 according to the present embodiment can obtain a higher static pressure than the impeller of the comparative example by bringing it close to the bellmouth 7 .

10 and 11 are perspective views showing another example of the impeller according to this embodiment from the bottom side.

As shown in FIGS. 10 and 11, the

impellers

23A and 23B according to this embodiment may include reinforcing

members

51A and 51B that connect the second parts 46 of the plurality of blade portions 32. As shown in FIGS. The reinforcing

members

51A and 51B are not the shrouds of conventional impellers that have a width in the radial direction and have a large dimensional difference between the outer diameter and the inner diameter, but are linear members such as steel wires. is.

The reinforcing

members

51A and 51B connect the second parts 46 of a pair of adjacent wing parts 32 and connect the second parts 46 of all the wing parts 32 . All wings 32 may be connected with a single reinforcing

member

51A, 51B, or all wings 32 may be connected with a plurality of reinforcing

members

51A, 51B that connect two or more but less than the total number of wings 32. It's okay to be

Further, the reinforcing member 51A may have a simple circular shape and may be fixed so as to make point contact with the second portion 46 of each wing portion 32 (Fig. 10). The reinforcing member 51B has a first straight portion 52 along the second portion 46 of each wing portion 32, and a second straight portion 53 bridging between a pair of adjacent wing portions 32. It may be fixed in line contact with the second portion 46 of the portion 32 (FIG. 11).

As described above, the blower device 6 according to the present embodiment includes the ring-shaped bell mouth 7, the flat downstream side 19 connected to the downstream end 7b of the bell mouth 7, and the downstream side 19 by sucking air from the bell mouth 7. and an impeller 23 for blowing out air in a direction along. The impeller 23 includes a main plate portion 31 extending radially and substantially parallel to the downstream side 19 and a plurality of open blade portions 32 . The outermost diameter D<b>2 drawn by the plurality of blade portions 32 is larger than the outermost diameter D<b>1 of the main plate portion 31 . The protruding ends 32a of the plurality of wings 32 protrude toward the upstream end 7a of the bell mouth 7 from the first portion 45 arranged close to the downstream side 19 and the downstream end 7b of the bell mouth 7. and a second portion 46 where the second portion 46 is located. Therefore, the blower device 6 can suppress turbulence in the flow of the air blown out from the impeller 23 and prevent a decrease in blowing efficiency. In addition, the blower 6 draws in air from the bell mouth 7 connected to the flat downstream side 19 and can generate an unturbulent air flow along the flat downstream side 19 . Further, the air blower 6 has a second portion 46 projecting toward the upstream end 7a of the bell mouth 7 from the downstream end 7b of the bell mouth 7, that is, the projection 47 of the wing portion 32. The air volume can be easily increased compared to a blower without the air blower.

Also, since the impeller 23 does not have a shroud, it can be integrally molded. Therefore, the impeller 23 eliminates factors that cause defects such as poor welding and poor adhesion when the separate shroud is joined to the wing portion. It is possible to reduce the imbalance amount of rotation balance.

Furthermore, the impeller 23 according to this embodiment includes a plurality of blade portions 32 that are connected only to the main plate portion 31 . Therefore, the impeller 23 can be easily made lighter than a conventional impeller having a shroud and a frame, and can eliminate obstacles to the air flow.

Further, the impeller 23 according to the present embodiment includes the wing portions 32 having root ends 32b that are continuous with the first side portions 35a of the respective petal portions 35, which are part of the edge of the main plate portion 31. Therefore, the impeller 23 can smoothly blow out the flow of air to which energy is given by the blade portion 32 .

In addition, the impeller 23 according to this embodiment has a first side portion 35a of the petal portion 35 and a second side portion 35b of the petal portion 35 facing each other across a gap in the circumferential direction of the main plate portion 31 . Therefore, the impeller 23 can blow out the air energized by the blades 32 through the gaps between the adjacent petals 35 . Such air flow improves the air blowing function of the impeller 23 . In addition, the gaps between the adjacent petals 35 improve the workability of each step in the hand lay-up method when integrally molding the impeller 23 and facilitate mold release.

Furthermore, the impeller 23 according to this embodiment includes a plurality of blade portions 32 each having a higher protrusion height than the hub portion 33 . Therefore, the impeller 23 can reduce the airflow resistance of the hub portion 33 and easily push out the airflow with the wing portions 32 .

Also, the exit angle β2 of the root end 32b of each blade 32 of the impeller 23 according to the present embodiment is larger than the entrance angle β1 of the root end 32b of the blade 32 . Therefore, the amount of air blown by the blower 6 is higher than that of an air blower having an impeller having a root portion in which the outlet angle β2 is smaller than the inlet angle β1. Also, the blower 6 can more easily provide a higher static pressure than a blower with an impeller whose outlet angle β2 is smaller than the inlet angle β1.

Furthermore, the root end 32b of each blade portion 32 of the impeller 23 according to the present embodiment has a linear shape. Therefore, the air blower 6 can easily set the outlet angle β2 of the root end 32b of each blade 32 to be larger than the inlet angle β1 of the root end 32b of the blade 32 .

Also, the thickness of each blade portion 32 of the impeller 23 according to this embodiment is thinner than the thickness of the main plate portion 31 . Therefore, the impeller 23 reduces the deformation of the blade portion 32 and prevents the reduction of the air volume due to the deformation of the blade portion 32 .

Further, the impeller 23 according to the present embodiment has a prime blade portion 32, and a pair of line segments L1 and L2 connecting the trailing edge 42 and the rotation center line C forms an angle of 25 degrees or more. Adjacent wings 32 are provided. Therefore, the impeller 23 reduces noise called blade pitch noise, reduces the air flow resistance generated between the adjacent blade portions 32 to improve the air volume, and furthermore, the manufacturability when integrally molding the impeller 23 improve.

Further, the impeller 23 according to this embodiment may include a reinforcing member 51 that connects the second portions 46 of the plurality of blade portions 32 . Therefore, even if the impeller 23 does not have a shroud, the weight of the entire impeller 23 is reduced, the influence of the centrifugal force on the blade portion 32 is reduced, the decrease in the air volume is suppressed, and the blade portion 32 is reduced. This prevents collision between the bell mouth 7 and the wings 32 due to deformation.

Therefore, according to the blower device 6 according to the present embodiment, air can be efficiently sucked from the bell mouth 7 and blown with high efficiency.

Although several embodiments of the invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the scope of the invention described in the claims and equivalents thereof.

DESCRIPTION OF SYMBOLS 1... Indoor unit 2... Heat exchanger 2a... Flat plate part 2b... Curved plate part 5... Housing 6... Air blower 7... Bell mouth 7a... Upstream end 7b... Downstream end 8 ... turbo fan 11 ... top plate 12 ... side plate 13 ... inclined plate 14 ... bottom plate 14a ... outer surface 14b ... inner surface 16 ... suction port 17 ... outlet 18 ... upstream side 19 ... downstream side, DESCRIPTION OF SYMBOLS 21... Rotating shaft 22...

Fan motor

23, 23A, 23B... Impeller 25... Fixture 31... Main plate part 32... Wing part 32a... Protruding end 32b... Root end 33... Hub part 35 Petal portion 35a First side portion 35b Second side portion 41 Front edge 42 Rear edge 45 First portion 46 Second portion 47 Convex portion 48 Linear edge 49... Curved edge, 51A, 51B... Reinforcement member, 52... First straight portion, 53... Second straight portion.

Claims

an annular bellmouth,
a flat downstream side continuous with the downstream end of the bell mouth;
an impeller that draws in air from the bell mouth and blows out the air in a direction along the downstream side;
The impeller is
a main plate portion substantially parallel to the downstream side and extending radially;
a plurality of open wing portions arranged in a ring projecting from the main plate portion toward the downstream side surface and the bell mouth;
The outermost diameter drawn by the plurality of wing portions is larger than the outermost diameter of the main plate portion,
The protruding ends of the plurality of wing portions include a first portion arranged close to the downstream side surface and a second portion protruding toward the upstream end of the bell mouth from the downstream end of the bell mouth. and a blower device.
2. The blower according to claim 1, wherein the exit angle of the root end of each of the blades connected to the main plate is greater than the entrance angle of the root end.
The air blower according to claim 1 or 2, wherein the base end of each of the blades connected to the main plate has a linear shape.
The air blower according to any one of claims 1 to 3, wherein the thickness of each of the blade portions is thinner than the thickness of the main plate portion.
the quantity of the plurality of wings is a prime number;
A first line segment connecting the trailing edge of the first blade portion and the rotation center line, and the trailing edge of the second blade portion adjacent to the first blade portion, when viewed from the direction along the rotation center line of the impeller. 5. The blower device according to claim 1, wherein an angle formed by a second line segment connecting the second line segment and the rotation center line is 25 degrees or more.
The blower device according to any one of claims 1 to 5, further comprising a reinforcing member that connects the second portions of the plurality of blade portions.