CN114922829B

CN114922829B - Centrifugal blower

Info

Publication number: CN114922829B
Application number: CN202210788222.9A
Authority: CN
Inventors: 铃木佑哉; 小坂翔; 小田修三; 今东升一
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2018-07-12
Filing date: 2019-06-13
Publication date: 2024-06-07
Anticipated expiration: 2039-06-13
Also published as: CN114922829A; WO2020012866A1

Abstract

The centrifugal fan (12) has a plurality of blades (121) and a separation plate (13), and sucks air from one side in the axial direction (DRa) of the fan axis. A suction port (14 a) and a blowout air passage (142 a) are formed in a fan housing (14), and the fan housing has a partition plate (15) that divides the blowout air passage into a first air passage (142 b) and a second air passage (142 c). The separation tube (18) is disposed radially inward of the centrifugal fan relative to the plurality of blades, and separates air passing through the suction port into inner air flowing radially inward of the separation tube and outer air flowing radially outward of the separation tube. The partition plate is configured such that outside air flows from the centrifugal fan into the first air passage and inside air flows into the second air passage. The separation tube is radially expanded as it moves to the other axial side, and is inclined with respect to the axial direction and radially expanded outward at the position of the other axial side end.

Description

Centrifugal blower

The application is a divisional application of the following patent applications:

Application number: 201980046253.3

Filing date: 2019, 06 and 13 days

The invention name is as follows: centrifugal blower

Cross-reference to related applications

The present application is based on japanese patent application nos. 2018-132470 and 2019-20806, both filed on 7 months and 12 days, and incorporated herein by reference.

Technical Field

The present invention relates to a centrifugal blower.

Background

Patent document 1 describes a centrifugal blower applied to an air conditioner for a vehicle having an inside/outside air double-layer flow. The centrifugal blower is capable of differentiating and simultaneously sucking two air streams from a single side. The centrifugal blower is provided with: a centrifugal fan having a plurality of blades and rotating around a fan axis; and a separation cylinder disposed radially inward of the centrifugal fan with respect to the plurality of blades.

The separation cylinder is substantially cylindrical with the fan axis as the center, and divides an air passage from the suction port of the scroll housing to the centrifugal fan into two air passages. The separation tube is formed to expand in the radial direction of the centrifugal fan from the suction port side toward the centrifugal fan side in the axial direction of the fan shaft center. The separation tube is positioned at the end of the centrifugal fan side, is orthogonal to the fan axis, and extends radially outward.

Prior art literature

Patent literature

Patent document 1: japanese patent application laid-open No. 2004-132342

In the centrifugal fan of patent document 1, the air flow from the suction port to the centrifugal fan is sucked between the blades of the centrifugal fan as well as from the axial direction to the radial direction outward along the curved shape of the separation tube. Since the direction of the air flow is forcibly changed by the separation cylinder in this way, a pressure loss occurs in the air flow along the separation cylinder in the vicinity of the end portion of the separation cylinder on the centrifugal fan side. The inventors have found the above matters as a result of detailed studies.

Disclosure of Invention

In view of the above, an object of the present invention is to provide a centrifugal fan capable of reducing pressure loss caused by an air flow in a separation tube.

In order to achieve the above object, according to one aspect of the present invention, a centrifugal blower includes:

a centrifugal fan having a plurality of blades and a separation plate arranged around a fan axis, and blowing out air sucked from one side in an axial direction of the fan axis toward an outside in a radial direction;

A fan housing that houses a centrifugal fan and that is formed with a suction port that is disposed on one side in an axial direction with respect to the centrifugal fan and through which air sucked into the centrifugal fan passes, and a blowout air passage that is disposed on an outer side in a radial direction with respect to the centrifugal fan and through which air blown out from the centrifugal fan flows, the fan housing having a partition plate that partitions the blowout air passage into a first air passage and a second air passage that is disposed on the other side in the axial direction with respect to the first air passage; and

A separation tube which is disposed radially inward of the centrifugal fan with respect to the plurality of blades and has a tubular shape facing the axial direction,

The separation cylinder separates air passing through the suction port into inside air flowing radially inward of the separation cylinder and outside air flowing radially outward of the separation cylinder,

The separation plate is in a plate shape expanding in a radial direction and is configured such that, between the plurality of blades, outside air flows on one side with respect to an axial direction of the separation plate, and inside air flows on the other side with respect to the axial direction of the separation plate,

The partition plate is configured such that outside air flows from the centrifugal fan into the first air passage, and inside air flows from the centrifugal fan into the second air passage,

The separation tube expands radially toward the other axial side, and has a shape inclined with respect to the axial direction and expanding radially outward at the other axial end position of the separation tube, which is the position of the other axial end of the separation tube.

In this way, for example, the direction of the air flow along the separation tube can be gradually changed to the direction between the blades, compared with the case where the separation tube has a shape that is orthogonal to the axial direction and expands to the outside in the radial direction at the other end position of the separation tube. Therefore, the pressure loss caused by bending the air flow along the separation tube can be reduced without enlarging the outer diameter of the separation tube.

The bracketed reference symbols for the respective components and the like indicate examples of correspondence between the components and the like and specific components and the like described in the embodiments described below.

Drawings

Fig. 1 is a view showing a schematic configuration of a centrifugal fan according to a first embodiment, and is a cross-sectional view showing a longitudinal section of the centrifugal fan taken along a plane including a fan axis of the centrifugal fan.

Fig. 2 is a partial enlarged view showing a portion II of fig. 1 in an enlarged manner.

Fig. 3 is a cross-sectional view schematically showing a first comparative example to be compared with the first embodiment by (a), and schematically showing a second comparative example to be compared with the first embodiment by (b).

Fig. 4 is a longitudinal sectional view showing a schematic structure of a centrifugal fan according to a third comparative example, and is a view corresponding to fig. 1.

Fig. 5 is a schematic view showing a separation tube, a separation plate, and a partition plate in a longitudinal cross-sectional view of the centrifugal blower of the fourth comparative example.

Fig. 6 is a schematic diagram showing a separation tube, a separation plate, and a partition plate in a longitudinal sectional view of the centrifugal blower according to the second embodiment.

Fig. 7 is a schematic diagram showing a separation tube, a separation plate, and a partition plate in a longitudinal sectional view of the centrifugal blower according to the third embodiment, and is a diagram corresponding to fig. 6.

Fig. 8 is a schematic diagram showing a separation tube, a separation plate, and a partition plate in a longitudinal sectional view of the centrifugal blower according to the fourth embodiment, and is a diagram corresponding to fig. 6.

Fig. 9 is a schematic diagram showing a separation tube, a separation plate, and a partition plate in a longitudinal sectional view of the centrifugal blower according to the fifth embodiment, and is a diagram corresponding to fig. 6.

Fig. 10 is a schematic diagram showing a separation tube, a separation plate, and a partition plate in a longitudinal sectional view of the centrifugal blower according to the sixth embodiment, and is a diagram corresponding to fig. 6.

Fig. 11 is a schematic diagram showing a separation tube, a separation plate, and a partition plate in a longitudinal sectional view of the centrifugal blower according to the seventh embodiment, and is a diagram corresponding to fig. 6.

Fig. 12 is a schematic diagram showing a separation tube, a separation plate, and a partition plate in a longitudinal sectional view of the centrifugal blower according to the eighth embodiment, and is a diagram corresponding to fig. 6.

Fig. 13 is a longitudinal sectional view showing a schematic configuration of a centrifugal fan according to a ninth embodiment, and is a view corresponding to fig. 1.

Fig. 14 is a vertical sectional view showing a schematic configuration of a centrifugal fan according to a tenth embodiment, and is a view corresponding to fig. 1.

Fig. 15 is a longitudinal sectional view showing a schematic configuration of a centrifugal fan according to an eleventh embodiment.

Fig. 16 is a partial enlarged view showing a portion XVI of fig. 15 in an enlarged manner.

Detailed Description

Hereinafter, embodiments will be described with reference to the drawings. In the following embodiments, the same or equivalent portions are denoted by the same reference numerals in the drawings.

(First embodiment)

The centrifugal fan 10 of the present embodiment shown in fig. 1 is applied to an air conditioner for a vehicle in which inside and outside air is two-layer flow. The vehicle air conditioner is capable of differentiating and simultaneously sucking in air inside a vehicle (i.e., inside air) and air outside the vehicle (i.e., outside air). In the following description, the centrifugal blower 10 will be simply referred to as the blower 10.

As shown in fig. 1, the blower 10 includes a centrifugal fan 12, a fan housing 14, a motor 16, and a separation tube 18. The centrifugal fan 12 rotates around a fan axis CL. As the centrifugal fan 12 rotates, the centrifugal fan 12 blows out air sucked from one side of the axial direction DRa of the fan axial center CL toward the outside in the radial direction DRr of the centrifugal fan 12. Fig. 1 shows a vertical section of the centrifugal fan 12, the fan housing 14, and the separation tube 18 taken in a plane including the fan axis CL, and in short, shows a vertical section of the blower 10 taken in a plane including the fan axis CL. In the following description, this vertical section is referred to as a vertical section of the blower 10 or a vertical section of fig. 1.

In the present embodiment, an axial direction DRa of the fan axial center CL, that is, an axial direction DRa of the centrifugal fan 12 is referred to as a fan axial direction DRa. The radial direction DRr of the fan axial center CL, that is, the radial direction DRr of the centrifugal fan 12 is referred to as a fan radial direction DRr. The fan radial DRr is a direction perpendicular to the fan axial direction DRa.

The centrifugal fan 12 has a plurality of blades 121, a main plate 122, a reinforcing member 123, and a separation plate 13. The plurality of blades 121 are arranged around the fan axis CL. The plurality of blades 121 have one end 121a as an end of one side of the fan axial direction DRa and the other end 121b as an end of the other side of the fan axial direction DRa, respectively.

The main plate 122 has a plate shape extending in the fan radial direction DRr. In short, the main plate 122 is disk-shaped with the fan axis CL as the center. The main plate 122 is disposed on the other side of the fan axial direction DRa with respect to the separation tube 18. The rotary shaft 161 of the motor 16 is connected to the center of the main plate 122 so as not to be rotatable relative to each other. The other ends 121b of the plurality of blades 121 are fixed to the outer side portion of the main plate 122 in the fan radial direction DRr.

In addition, the main plate 122 has a main plate guide surface 122a on one side in the fan axial direction DRa. The main plate guide surface 122a faces one side of the fan axial direction DRa and expands in the fan radial direction DRr.

The reinforcing member 123 reinforces the centrifugal fan 12. The reinforcing member 123 is annular about the fan axis CL. The reinforcing member 123 is fixed to a radially outer portion of each of the plurality of blades 121 on the one end 121a side.

The separation plate 13 separates air flowing between the plurality of blades 121 into air flowing on one side of the fan axial direction DRa with respect to the separation plate 13 and air flowing on the other side of the fan axial direction DRa with respect to the separation plate 13.

Specifically, the separation plate 13 extends annularly around the fan axis CL while intersecting each of the plurality of blades 121. The separation plate 13 is in the form of a plate extending in the fan radial direction DRr. Each of the plurality of blades 121 and the separation plate 13 are fixed to each other at a portion where the blades 121 and the separation plate 13 intersect. In the present embodiment, the plurality of blades 121, the main plate 122, the reinforcing member 123, and the separation plate 13 are formed as an integrally molded product formed of an integral resin.

As shown in fig. 1 and 2, the separation plate 13 has a separation plate outer end 131 provided outside the fan radial direction DRr and a separation plate inner end 132 provided inside the fan radial direction DRr. The separating plate outer end 131 has an outer end face 131a facing the outside of the fan radial direction DRr. The outer end surface 131a is an annular end surface extending from one side to the other side of the fan axial direction DRa at a position of an outer end of the separation plate 13 in the fan radial direction DRr.

In addition, the separation plate inner end 132 has an inner end surface 132a facing the inner side of the fan radial direction DRr. The inner end surface 132a is an annular end surface extending from one side to the other side of the fan axial direction DRa at a position of an inner end of the separation plate 13 in the fan radial direction DRr.

In addition, the separation plate inner end 132 is located on one side of the fan axial direction DRa with respect to the separation plate outer end 131. In detail, the separation plate 13 extends continuously so as to be located on the other side of the fan axial direction DRa as being located on the outer side of the fan radial direction DRr. The separation plate 13 is inclined with respect to the fan axis CL in the vertical section of fig. 1, and extends linearly from the separation plate inner end 132 to the separation plate outer end 131.

In the present embodiment, the vane type of the vane-side portion 121c, which is a portion on the side of the separation plate 13 in the fan axial direction DRa, is the vane type of the sirocco fan. Similarly, the blade type of the blade other side portion 121d, which is the other side portion with respect to the fan axial direction DRa of the separation plate 13, of the blades 121 is also the blade type of the sirocco fan.

The fan case 14 functions as a housing constituting a casing of the blower 10, and the centrifugal fan 12 is housed inside the fan case 14. The fan housing 14 is formed with a suction port 14a through which air sucked into the centrifugal fan 12 passes. The suction port 14a is disposed on one side of the centrifugal fan 12 in the fan axial direction DRa.

The fan housing 14 has a flare 141 that forms a peripheral edge of the suction port 14 a. The cross-sectional shape of the bell mouth 141 is circular arc-shaped so that air smoothly flows through the suction port 14 a.

The fan housing 14 includes an air passage forming portion 142 and a partition plate 15. The air passage forming portion 142 is provided with a blown-out air passage 142a provided on the outer side in the fan radial direction DRr with respect to the centrifugal fan 12. In the blown-out air passage 142a, air blown out from the centrifugal fan 12 flows together. For example, the blown air passage 142a is formed in a spiral shape around the centrifugal fan 12. Also, the fan housing 14 is also referred to as a scroll housing.

The air passage forming portion 142 has an outer peripheral wall 143 extending in the fan axial direction DRa around the centrifugal fan 12. The outer peripheral wall 143 faces the blown-out air passage 142a from the outside in the fan radial direction DRr.

The partition plate 15 is provided inside the blown-out air passage 142 a. The partition plate 15 divides the blown-out air passage 142a into a first air passage 142b arranged on one side of the fan axial direction DRa with respect to the partition plate 15 and a second air passage 142c arranged on the other side of the fan axial direction DRa with respect to the partition plate 15.

The partition plate 15 is a plate-like member extending in the fan radial direction DRr. The partition plate 15 has a partition plate outer end 151 provided outside the fan radial direction DRr and a partition plate inner end 152 provided inside the fan radial direction DRr. The divider plate outer end 151 is connected to the outer peripheral wall 143. That is, the partition plate 15 extends from the outer peripheral wall 143 toward the centrifugal fan 12 with the partition plate outer end 151 as a base end. In the present embodiment, the air passage forming portion 142 and the partition plate 15 are formed as an integrally molded product formed as a single piece of resin. The plate thickness of the partition plate 15, the plate thickness of the separation plate 13, and the plate thickness of the separation tube 18 are, for example, the same or substantially the same.

The partition plate inner end 152 has a partition plate end face 152a facing the inner side of the fan radial direction DRr. The partition plate end surface 152a is an annular end surface extending from one side to the other side in the fan axial direction DRa at the position of the inner end of the partition plate 15 in the fan radial direction DRr.

The partition plate 15 has a partition plate outer portion 153 and a partition plate inner portion 154, and the partition plate inner portion 154 is disposed inside the fan radial direction DRr with respect to the partition plate outer portion 153 and is connected in series with the partition plate outer portion 153. The divider plate outer section 153 includes a divider plate outer end 151 and the divider plate inner section 154 includes a divider plate inner end 152.

The partition plate outer portion 153 is formed so as not to be displaced in the fan axial direction DRa but to expand in the fan radial direction DRr. That is, the partition plate outer portion 153 has a shape that expands in a direction orthogonal to the fan axial direction DRa. In other words, the partition plate outer portion 153 has a shape that expands in a direction orthogonal to the fan axial direction DRa. Therefore, the partition plate 15 has a shape that expands in a direction orthogonal to the fan axial direction DRa at the position of the partition plate outer end 151.

In contrast, the partition plate inner portion 154 extends so as to be located on the other side in the fan axial direction DRa as it extends outward in the fan radial direction DRr. The partition plate inner portion 154 extends obliquely and linearly with respect to the fan axis CL in the vertical cross section of fig. 1. Accordingly, the partition plate inner portion 154 is coupled to the partition plate outer portion 153 in such a manner as to be bent at the boundary of the partition plate inner portion 154 and the partition plate outer portion 153.

That is, in the vertical cross section of fig. 1, the partition plate 15 is formed so that the angle between the partition plate 15 and the fan axis CL becomes closer to the angle orthogonal to the fan axis CL stepwise as going from the partition plate inner end 152 toward the outside in the fan radial direction DRr.

Also, the partition plate inner portion 154 and the partition plate outer portion 153 are portions located on the other side of the fan axial direction DRa with respect to the partition plate inner end 152. Further, the partition plate outside portion 153 is a portion of the partition plate 15 located on the other-most side of the fan axial direction DRa. The partition plate outer end 151 is located on the other side of the fan axial direction DRa from the partition plate inner end 152.

In the vertical cross section of fig. 1, the inclination angle of the partition plate inner portion 154 with respect to the fan axis CL is the same as the inclination angle of the separation plate 13.

The motor 16 is an electric driving device for rotating the centrifugal fan 12. The motor 16 has a rotation shaft 161 and a main body 162. The rotation shaft 161 extends from the main body 162 toward one side of the fan axial direction DRa. The centrifugal fan 12 rotates by the rotation of the rotation shaft 161. The main body 162 is fixed to the fan housing 14. The main body 162, the fan housing 14, and the separation barrel 18 are non-rotating members that do not rotate.

The separation tube 18 is a tubular member extending in the fan axial direction DRa. In short, the separation tube 18 has a tube shape facing the fan axial direction DRa. The separation tube 18 has a tube shape in which one end and the other end of the fan axial direction DRa are open. The separation tube 18 is disposed inside the fan radial direction DRr with respect to the flare 141 and the plurality of blades 121 of the centrifugal fan 12. The separation tube 18 is disposed such that a part of the separation tube 18 passes through the suction port 14a and is inserted into the fan housing 14. The separation cartridge 18 is fixed with respect to the fan housing 14, for example.

With such a shape and arrangement, the separation tube 18 separates the air flow from the suction port 14a toward the centrifugal fan 12 into two air flows. The separation tube 18 divides the air passage from the suction port 14a to the centrifugal fan 12 into two air passages. That is, the separation tube 18 separates the air passing through the suction port 14a into inside air flowing inside the fan radial direction DRr with respect to the separation tube 18 and outside air flowing outside the fan radial direction DRr with respect to the separation tube 18. In fig. 1, the flow of the outside air is indicated by an arrow Fo, and the flow of the inside air is indicated by an arrow Fi.

The separation tube 18 is formed so as to expand in the fan radial direction DRr toward the other side in the fan axial direction DRa, so that the inside air and the outside air guide vane 121 are interposed between each other. That is, on the other side of the fan axial direction DRa in the separation tube 18, the diameter of the separation tube 18 increases from the one-side end toward the other-side end of the fan axial direction DRa.

Specifically, the separation tube 18 has one side portion 183 and the other side portion 184, and the other side portion 184 is disposed on the other side of the fan axial direction DRa with respect to the one side portion 183 and is connected in series with the one side portion 183. The one-side portion 183 extends along the fan axial direction DRa without changing the diameter of the separation tube 18.

In contrast, the other side portion 184 of the separation tube 18 extends from one side to the other side in the fan axial direction DRa while being bent so as to expand outward in the fan radial direction DRr. The separation tube 18 has a shape that is inclined with respect to the fan axial direction DRa and that expands outward in the fan radial direction DRr at a separation tube other end position PTa that is a position of the other end of the separation tube 18 in the fan axial direction DRa. The separation cylinder other end position PTa is also the position of the other side end of the fan axial direction DRa of the other side portion 184.

In addition, the separation tube 18 has a separation tube other end 185 provided on the other side of the fan axial direction DRa. The other end 185 of the separating tube is included in the other side portion 184 of the separating tube 18 and is also a radially outer end of the separating tube 18 that is disposed outside of the fan radial DRr.

The separator bowl other end 185 has a separator bowl end face 185a facing the outside of the fan radial DRr. The separation cylinder end surface 185a is an annular end surface extending from one side to the other side of the fan axial direction DRa at the separation cylinder other end position PTa.

Further, the separation tube 18 has the cylindrical shape described above, and therefore has a separation tube outer side surface 181 configured as an outer side wall surface of the cylindrical shape and a separation tube inner side surface 182 configured as an inner side wall surface of the cylindrical shape. Both the separation barrel outer side 181 and the separation barrel inner side 182 are formed from one side portion 183 to the other side portion 184.

The separation cylinder outer side 181 includes an outward facing surface 181a facing the outside of the fan radial DRr and extends to the separation cylinder other end position PTa. In other words, the separator bowl outer side 181 includes the outward facing surface 181a and extends to the other end 185 of the separator bowl. The outward surface 181a is an outer side wall surface of the one side portion 183 of the separation tube 18, and extends along the fan axis CL in the fan axial direction DRa.

The inner surface 182 of the separation cylinder includes an inward surface 182a facing the inner side of the fan radial direction DRr and extends to the other end position PTa of the separation cylinder. In other words, the separator bowl inner side 182 includes the inward facing surface 182a and extends to the other end 185 of the separator bowl. The inward surface 182a is an inner wall surface of the one side portion 183 of the separation tube 18, and extends along the fan axis CL in the fan axial direction DRa.

The main plate guide surface 122a guides the inside air to flow toward the outside in the fan radial direction DRr on the air flow upstream side with respect to the plurality of blades 121 as indicated by an arrow Fi. In the vertical cross section of fig. 1, when the intersection point Pn at which the normal Ln of the cylinder inner surface 182 at the cylinder other end position PTa intersects the main plate guide surface 122a is defined as the main plate guide surface intersection point Pn, the following description will be made. That is, in the vertical cross section of fig. 1, the tangential direction D1t of the inner surface 182 of the separator obtained at the other end position PTa of the separator is oriented in the same direction as the tangential direction D2t of the main plate guide surface 122a obtained at the main plate guide surface intersection point Pn. Specifically, the tangential direction D1t of the inner surface 182 of the separating cylinder is parallel to the tangential direction D2t of the main plate guiding surface 122 a.

As shown in fig. 1, the separation plate 13 is configured to separate the flow of outside air indicated by an arrow Fo and the flow of inside air indicated by an arrow Fi in the fan axial direction DRa on the downstream side of the air flow of the separation tube 18. That is, the separation plate 13 is configured such that outside air flows as indicated by arrow Fo on one side with respect to the fan axial direction DRa of the separation plate 13 and inside air flows as indicated by arrow Fi on the other side with respect to the fan axial direction DRa of the separation plate 13 between the plurality of blades 121.

The partition plate 15 is disposed so as to separate the flow of outside air indicated by the arrow Fo and the flow of inside air indicated by the arrow Fi in the fan axial direction DRa on the downstream side of the air flow of the centrifugal fan 12. That is, the partition plate 15 is configured such that outside air flows from the centrifugal fan 12 into the first air passage 142b as indicated by arrow Fo, and inside air flows into the second air passage 142c as indicated by arrow Fi.

In short, the separation plate 13 and the separation plate 15 are respectively configured to suppress mixing of outside air and inside air on the downstream side of the air flow with respect to the separation tube 18.

Further, as shown in fig. 1, gaps are respectively provided between the separation plate 13 and the separation tube 18, and between the separation plate 13 and the separation plate 15 to allow relative rotation. Accordingly, the following will explain in detail. That is, among the plurality of blades 121, outside air flows significantly more on one side than inside air with respect to the fan axial direction DRa of the separation plate 13, and inside air flows significantly more on the other side than outside air with respect to the fan axial direction DRa of the separation plate 13. Further, the outside air flows from the centrifugal fan 12 into the first air passage 142b in an amount that is significantly larger than the inside air, and the inside air flows into the second air passage 142c in an amount that is significantly larger than the outside air.

Specifically, as shown in fig. 2, in order to separate the outside air and the inside air as described above, the other end 132b of the inside end surface 132a of the separation plate 13 is positioned on the other side than the one end 185b of the separation cylinder end surface 185a in the fan axial direction DRa.

Specifically, in the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation tube 18 in a case where the separation tube other end 185 and the separation plate inner end 132 are linearly complemented to connect each other. The "continuous connection" means not only connection without any step difference or meandering but also connection of the separation plate 13 and the separation tube 18 to a degree that a small step difference or a small meandering occurs in comparison with the plate thickness of the separation plate 13 and the separation tube 18. This is also true in the "continuous connection" between the separation plate 13 and the separation plate 15 described later.

In the fan axial direction DRa, the end 131b of the outer end surface 131a of the separation plate 13 is located on one side than the end 152b of the other side of the separation plate end surface 152 a. Specifically, in the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the partition plate 15 in a case where the separation plate outer end 131 and the separation plate inner end 152 are linearly complemented to connect each other.

In the blower 10 of the present embodiment configured as described above, when the centrifugal fan 12 is rotated by the motor 16, air is sucked from the side of the axial direction DRa of the centrifugal fan 12 to the inside in the fan radial direction DRr of the centrifugal fan 12. The sucked air is blown out from the centrifugal fan 12 to the outside in the fan radial direction DRr. The air blown out from the centrifugal fan 12 flows through the blown-out air passage 142a of the fan housing 14, and then is blown out from the outlet of the fan housing 14.

At this time, as shown in fig. 1, inside the blower 10, outside air indicated by an arrow Fo and inside air indicated by an arrow Fi flow in a separated state through the separation tube 18, the separation plate 13, and the separation plate 15.

The air blown out from the blower 10 flows through an air conditioning case of an air conditioning device for a vehicle, not shown. A temperature regulator for regulating the air temperature is disposed in the air conditioning case. The air blown out from the blower 10 is blown out into the vehicle interior after the temperature thereof is adjusted by the temperature regulator. Even in the air-conditioning case, the flow of outside air and the flow of inside air are maintained in a separated state. After the temperature of each of the two air streams is adjusted, the two air streams are blown out into the vehicle interior from, for example, different air outlets.

As described above, according to the present embodiment, as shown in fig. 1, the separation tube 18 expands in the fan radial direction DRr as it moves to the other side in the fan axial direction DRa. The separation tube 18 is inclined with respect to the fan axial direction DRa at the separation tube other end position PTa of the separation tube 18 and is expanded outward in the fan radial direction DRr.

Therefore, for example, compared with the blower 91 of the first comparative example shown in fig. 3 (a), the radius of curvature Rc of the other side portion 184 of the separation tube 18 that is expanded can be increased. That is, the direction of the air flow along the separation tube 18 can be changed to be directed between the blades 121 more gradually than the blower 91 of the first comparative example. Therefore, in the present embodiment, it is not necessary to enlarge the outer diameter Dcr of the separation tube 18, and the pressure loss due to the air flow along the separation tube 18 by bending can be reduced.

Here, as in the blower 92 of the second comparative example shown in fig. 3 (b), the outer diameter Dcr can be enlarged as indicated by the arrow Acr with respect to the blower 91 of the first comparative example, whereby the radius of curvature Rc of the other side portion 184 can be increased. However, if the size of the blower 92 is increased in this way, the size is enlarged. In contrast, the separation tube 18 of the present embodiment shown in fig. 1 has a shape that is inclined with respect to the fan axial direction DRa and that expands outward in the fan radial direction DRr at the separation tube other end position PTa of the separation tube 18. Therefore, the radius of curvature Rc of the other side portion 184 can be increased without enlarging the outer diameter Dcr of the separation tube 18.

As shown in fig. 3 (a) and (b), the separation tube 18 of each of the blowers 91 and 92 of the first and second comparative examples has a shape extending outward in the fan radial direction DRr at the separation tube other end position PTa (see fig. 1) of the separation tube 18, which is orthogonal to the fan axial direction DRa. In fig. 3 (a) and (b), only one side of the vertical section of the blowers 91 and 92 with respect to the fan axis CL is shown by being extracted, and the same applies to the later-described drawings similar to fig. 3.

In addition, according to the present embodiment, as shown in fig. 1 and 2, in the separation plate 13, the separation plate inner end 132 is located on one side of the fan axial direction DRa with respect to the separation plate outer end 131. Therefore, the pressure loss caused by the outside air flowing along the separation cylinder outer side surface 181 and having the velocity component toward the other side in the fan axial direction DRa hitting the separation plate 13 can be reduced.

In addition, according to the present embodiment, the partition plate 15 has the partition plate outside portion 153, which partition plate outside portion 153 is included in a portion located on the other side of the fan axial direction DRa with respect to the partition plate inside end 152.

Therefore, it is difficult to prevent the air blown out from the plurality of blades 121 from flowing outside the fan radial direction DRr while having a velocity component directed to the other side of the fan axial direction DRa around the partition plate inner end 152. Therefore, the pressure loss due to the outside air blown out from between the blades 121 hitting the partition plate 15 can be reduced.

Further, according to the present embodiment, the fan case 14 has the outer peripheral wall 143 facing the blown-out air passage 142a from the outer side surface in the fan radial direction DRr. The partition plate 15 has a partition plate outer end 151 provided outside the fan radial direction DRr and connected to the outer peripheral wall 143. The partition plate 15 is formed at the position of the partition plate outer end 151 so as to extend in a direction perpendicular to the fan axial direction DRa.

Therefore, the following description can be made, as compared with the blower 93 of the third comparative example in which the partition plate 15 is formed in a shape that extends outward in the fan radial direction DRr while being inclined at the position of the partition plate outer end 151 and toward the other side in the fan axial direction DRa, as shown in fig. 4. That is, in the present embodiment, compared to the blower 93 of the third comparative example in fig. 4, the direction of the outside air reaching the outer peripheral wall 143 of the fan housing 14 along the partition plate 15 can be suppressed from rapidly changing, for example, as indicated by the arrow Fr in fig. 4. As a result, the output of the blower 10 can be further improved.

In addition, according to the present embodiment, as shown in fig. 1 and 2, in the vertical section of the blower 10, the partition plate inner portion 154 includes the partition plate inner end 152 and linearly extends and is inclined so as to be located further to the other side in the fan axial direction DRa than to the outside in the fan radial direction DRr. On the other hand, the partition plate outer portion 153 has a shape that expands in a direction orthogonal to the fan axial direction DRa. That is, in the vertical cross section of the blower 10, the partition plate 15 is formed so that the angle between the partition plate 15 and the fan axis CL becomes closer to the angle orthogonal to the fan axis CL stepwise as going from the partition plate inner end 152 toward the outside in the fan axial direction DRr.

Therefore, the direction of the air flowing along the partition plate 15 can be gradually changed to a direction which is approximately orthogonal to the fan axis and which is directed to the outside in the fan radial direction DRr. As a result, for example, the pressure loss caused by the outside air blown out from the centrifugal fan 12 as indicated by arrow Fo hitting the partition plate 15 can be reduced.

In addition, according to the present embodiment, as shown in fig. 2, the other end 132b of the inner end surface 132a of the separation plate 13 is positioned on the other side than the one end 185b of the separation cylinder end surface 185a in the fan axial direction DRa. Therefore, compared to the case where the end 185b on one side of the separator tube end surface 185 is located on the opposite side of the end 132b on the other side of the inner end surface 132, the mixing of the two air streams separated by the separator tube 18 through the gap between the separator tube 18 and the separation plate 13 is suppressed.

In addition, according to the present embodiment, as shown in fig. 2, in the fan axial direction DRa, the end 131b on one side of the outer end surface 131a of the separation plate 13 is located on one side of the end 152b on the other side of the separation plate end surface 152 a. Therefore, compared to the case where the end 131b on the one side of the outer end surface 131a is located on the other side of the partition plate end surface 152a, the two air flows separated by the separation plate 13 are suppressed from being mixed through the gap between the partition plate 15 and the separation plate 13.

In addition, according to the present embodiment, in the cross-sectional view of fig. 1, an intersection point Pn at which the normal Ln of the separation cylinder inner side surface 182 at the separation cylinder other end position PTa intersects with the main plate guide surface 122a is set as a main plate guide surface intersection point Pn. In this case, in the cross-sectional view of fig. 1, the tangential direction D1t of the inner surface 182 of the separator obtained at the other end position PTa of the separator and the tangential direction D2t of the main plate guide surface 122a obtained at the main plate guide surface intersection point Pn are oriented in the same direction.

Here, in the flow path formed between the separation tube inner surface 182 and the main plate guide surface 122a and through which the inner air flows, the change in the circumferential length of the flow path cross section around the fan axial center CL increases as the circumferential length increases toward the downstream side, so that the flow path cross section increases toward the downstream side. Further, assuming that the tangential direction D1t of the inner surface 182 of the separation tube is oriented closer to the direction orthogonal to the fan axis than the tangential direction D2t of the main plate guide surface 122a, the variation in the height of the flow path cross section shown in the vertical section of fig. 1 contributes to the expansion of the flow path cross section.

In contrast, in the present embodiment, the change in the height of the flow path cross section shown in the vertical section of fig. 1 is less likely to contribute to the expansion of the flow path cross section. Therefore, the rate of change in the flow path cross-sectional area of the flow path through which the inside air flows can be reduced as compared with the virtual case described above.

Fig. 5 shows a fourth comparative example blower 94 compared with the present embodiment. In the blower 94 of the fourth comparative example, the position in the fan axial direction DRa coincides between the separator tube other end 185 and the separator inner end 132 and also coincides between the separator inner end 152 and the separator outer end 131.

In contrast, according to the present embodiment, as compared with the fourth comparative example described above, the position of the separation plate inner end 132 is offset to the other side in the fan axial direction DRa with respect to the position of the separation cylinder other end 185, as shown in fig. 1 and 2. In the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation tube 18 in a case where the separation tube other end 185 and the separation plate inner end 132 are linearly complemented to connect each other.

Therefore, in the present embodiment, compared with the fourth comparative example of fig. 5, the outside air and the inside air flowing along the separation tube 18 can be smoothly caused to flow along the separation plate 13. The gap between the separation tube 18 and the separation plate 13 can be made to have a minimum size (specifically, zero) in a direction perpendicular to the flow of the outside air and the inside air indicated by arrows Fo and Fi in fig. 1 at the position of the gap. Therefore, for example, compared with the fourth comparative example, the separability of the outside air from the inside air while being separated can be improved.

In addition, according to the present embodiment, as compared with the fourth comparative example described above, as shown in fig. 1 and 2, the position of the partition plate inner end 152 is deviated to the other side in the fan axial direction DRa than the position of the partition plate outer end 131. In the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation plate 15 in a case where the separation plate outer end 131 and the separation plate inner end 152 are linearly complemented to connect each other.

Therefore, in the present embodiment, compared with the fourth comparative example of fig. 5, the outside air and the inside air flowing along the separation plate 13 can be smoothly caused to flow along the separation plate 15. The gap between the partition plate 15 and the separation plate 13 can be made to have a minimum size (specifically, zero) in a direction perpendicular to the flow of the outside air and the inside air indicated by arrows Fo and Fi in fig. 1 at the position of the gap. Therefore, for example, compared with the fourth comparative example, the separability of the outside air from the inside air while being separated can be improved.

(Second embodiment)

Next, a second embodiment will be described. In this embodiment, points different from the first embodiment described above will be mainly described. The same or equivalent parts as those of the above embodiments will be omitted or simplified. This is also the same as in the description of the embodiment described later.

As shown in fig. 6, in the present embodiment, the relative positional relationship between the separation tube 18 and the separation plate 13 and the separation plate 15 in the fan axial direction DRa is different from that in the first embodiment.

Specifically, in the fan axial direction DRa, the end 132c of the inner end surface 132a of the separation plate 13 is positioned on the other side than the end 185c of the separation cylinder end surface 185 a. In the fan axial direction DRa, the other end 131c of the outer end surface 131a of the separation plate 13 is located on one side of the one end 152c of the separation plate end surface 152 a.

Therefore, in the vertical section of the blower 10, when the other end 185 of the separator and the inner end 132 of the separator are linearly complemented to connect, the air flows between the separator 13 and the separator 18, and the separator 13 and the separator 18 cannot be connected continuously. This is also the same in relation to the relative positions of the separating plate 13 and the separating plate 15.

The present embodiment is similar to the first embodiment except for the above-described matters, and in the present embodiment, the effects obtained by the configuration common to the first embodiment can be obtained as in the first embodiment.

In addition, according to the present embodiment, in the fan axial direction DRa, the end 132c of the inner end surface 132a of the separation plate 13 on one side is located on the other side than the end 185c of the separation cylinder end surface 185a on the other side. Therefore, when the outside air flows along the separation plate 13 as indicated by the arrow Fa, the output of the blower 10 can be improved as compared with the fourth comparative example of fig. 5, for example, by utilizing the inertia of the outside air flowing as indicated by the arrow Fit toward the other side of the fan axial direction DRa.

(Third embodiment)

Next, a third embodiment will be described. In this embodiment, points different from the first embodiment described above will be mainly described.

As shown in fig. 7, in the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation tube 18 in a case where the separation tube other end 185 and the separation plate inner end 132 are linearly complemented to connect. In the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation plate 15 in a case where the separation plate outer end 131 and the separation plate inner end 152 are linearly complemented to connect each other. In this regard, the present embodiment is the same as the first embodiment.

However, as shown in fig. 7, in the present embodiment, the shapes of the separation plate 13 and the partition plate 15 are different from those of the first embodiment. Arrows F1o and F2o in fig. 7 indicate the flow of outside air.

Specifically, in the vertical cross section of the blower 10, the separation plate 13 of the present embodiment does not extend linearly. In this vertical cross section, the separation plate 13 is curved so as to expand in the fan radial direction DRr at an angle closer to the direction orthogonal to the fan axis CL as it goes from the separation plate inner end 132 toward the separation plate outer end 131. In other words, in the vertical cross section of the blower 10, the separation plate 13 is curved so that the tangential direction of the separation plate 13 approaches the direction orthogonal to the fan axis CL as it goes from the separation plate inner end 132 toward the separation plate outer end 131.

The separation plate 13 extends inward of the fan radial direction DRr and obliquely toward one side of the fan axial direction DRa at the position of the separation plate inner end 132. The separation plate 13 extends in a direction perpendicular to the fan axis CL at the position of the separation plate outer end 131.

Therefore, the center Crf of the radius of curvature Rf of the separation plate 13 shown in the vertical cross section of the blower 10 is located on one side of the separation plate 13 in the fan axial direction DRa. The separation plate 13 shown in this longitudinal section is curved, for example, over the entire width of the fan radial direction DRr.

The partition plate 15 of the present embodiment is not formed to be meandering in the vertical section of the blower 10. As shown in fig. 7, in a vertical cross section of the blower 10, the partition plate 15 extends linearly in the fan radial direction DRr, perpendicularly to the fan axial center CL (see fig. 1), from the partition plate inner end 152 to the partition plate outer end 151.

The present embodiment is the same as the first embodiment except for the above description. In the present embodiment, the same effects as those obtained by the configuration common to the first embodiment described above can be obtained as in the first embodiment.

In addition, according to the present embodiment, in the vertical cross section of the blower 10, the separation plate 13 is curved so as to expand in the fan radial direction DRr at an angle closer to the direction orthogonal to the fan axis CL as it goes from the separation plate inner end 132 toward the separation plate outer end 131. Therefore, the pressure loss caused by the outside air flowing along the separation tube 18 and having the velocity component toward the other side of the fan axial direction DRa hitting the separation plate 13 can be reduced. Further, by making the outside air follow the separation plate 13, the velocity component of the outside air toward the other side in the fan axial direction DRa can be reduced, and the outside air can be guided to the outside in the fan radial direction DRr.

Although this embodiment is a modification of the first embodiment, this embodiment can be combined with the second embodiment described above.

(Fourth embodiment)

Next, a fourth embodiment will be described. In this embodiment, points different from the third embodiment described above will be mainly described.

As shown in fig. 8, in the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation tube 18 in a case where the separation tube other end 185 and the separation plate inner end 132 are linearly complemented to connect. In this regard, the present embodiment is the same as the third embodiment.

However, in the present embodiment, in the case where the air blower 10 is linearly complemented in the vertical section so as to connect the separation plate outer end 131 and the separation plate inner end 152, the complemented portion 135 is continuously connected to the separation plate 13, but the complemented portion 135 is zigzag connected to the separation plate 15. That is, when the above is complemented, the separation plate 13 and the separation plate 15 cannot be continuously connected. In this regard, the present embodiment is different from the third embodiment.

In the present embodiment, the shape of the separation plate 13 is different from that of the third embodiment, and the separation plate 13 of the present embodiment is not curved in the vertical cross section of the blower 10.

Specifically, in the present embodiment, in the vertical cross section of the blower 10, the separation plate 13 is formed so that the angle formed between the separation plate 13 and the fan axis CL becomes closer to the angle orthogonal to the fan axis CL stepwise as it goes from the separation plate inner end 132 toward the separation plate outer end 131.

In detail, the separation plate 13 has a separation plate outer portion 133 and a separation plate inner portion 134, and the separation plate inner portion 134 is disposed inside the fan radial direction DRr with respect to the separation plate outer portion 133 and is connected in series with the separation plate outer portion 133. The separator outboard portion 133 includes a separator outboard end 131 and the separator inboard portion 134 includes a separator inboard end 132.

In the vertical cross section of the blower 10, the separation plate outer portion 133 and the separation plate inner portion 134 linearly extend so as to be located on the other side in the fan axial direction DRa as going outward in the fan radial direction DRr. However, in this vertical cross section, the angle formed by the separation plate outer portion 133 and the fan axis CL is closer to the angle orthogonal to the fan axis CL than the angle formed by the separation plate inner portion 134 and the fan axis CL. Therefore, the separation plate inner portion 134 is coupled to the separation plate outer portion 133 in such a manner as to meander at the boundary of the separation plate inner portion 134 and the separation plate outer portion 133.

The present embodiment is the same as the third embodiment except for the above description. In the present embodiment, the same effects as those obtained by the configuration common to the third embodiment described above can be obtained as in the third embodiment.

In addition, according to the present embodiment, in the vertical cross section of the blower 10, the separation plate 13 is formed so that the angle formed between the separation plate 13 and the fan axis CL becomes closer to the angle orthogonal to the fan axis CL stepwise as it goes from the separation plate inner end 132 toward the separation plate outer end 131. Therefore, the pressure loss caused by the outside air flowing along the separation tube 18 and having the velocity component toward the other side of the fan axial direction DRa hitting the separation plate 13 can be reduced. Further, by making the outside air follow the separation plate 13, the velocity component of the outside air toward the other side in the fan axial direction DRa can be reduced, and the outside air can be guided to the outside in the fan radial direction DRr.

(Fifth embodiment)

Next, a fifth embodiment will be described. In this embodiment, points different from the first embodiment described above will be mainly described.

As shown in fig. 9, in the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation tube 18 in a case where the separation tube other end 185 and the separation plate inner end 132 are linearly complemented to connect. In the vertical section of the blower 10, the separation plate 13 is arranged to be continuously connected to the separation plate 15 in a case where the separation plate outer end 131 and the separation plate inner end 152 are linearly complemented to connect each other. In this regard, the present embodiment is the same as the first embodiment.

However, as shown in fig. 9, in the present embodiment, the shape of the partition plate 15 is different from that of the first embodiment.

Specifically, in the vertical cross section of the blower 10, the partition plate 15 of the present embodiment is curved so as to expand in the fan radial direction DRr at an angle approaching the direction orthogonal to the fan axial center CL as going from the partition plate inner end 152 toward the outside of the fan radial direction DRr. In other words, in the vertical cross section of the blower 10, the partition plate 15 is curved so that the tangential direction of the partition plate 15 approaches the direction orthogonal to the fan axis CL as going from the partition plate inner end 152 toward the outside in the fan radial direction DRr.

Specifically, in the vertical section of the blower 10, the partition plate outer portion 153 and the partition plate inner portion 154 are connected to each other continuously without being bent at their boundaries. The partition plate outer portion 153 extends linearly in the fan radial direction DRr across its entire length, perpendicularly to the fan axial center CL (see fig. 1).

On the other hand, the partition plate inner portion 154 is curved so as to expand in the fan radial direction DRr at an angle closer to the direction orthogonal to the fan axial center CL as it goes to the outside of the fan radial direction DRr. Also, the partition plate inner portion 154 is located at the partition plate inner end 152, toward the inside of the fan radial direction DRr, and extends obliquely toward one side of the fan axial direction DRa. The partition plate inner portion 154 extends in a direction perpendicular to the fan axis CL at a position where it is connected to the partition plate outer portion 153.

Therefore, the center Crd of the radius of curvature Rd of the partition plate inner portion 154 shown in the longitudinal section of the blower 10 is located on one side of the partition plate 15 in the fan axial direction DRa.

In addition, according to the present embodiment, in the vertical cross section of the blower 10, the partition plate 15 is curved so as to expand in the fan radial direction DRr at an angle approaching the direction orthogonal to the fan axis CL as going from the partition plate inner end 152 toward the outside of the fan radial direction DRr. Therefore, the direction of the air flowing along the partition plate 15 can be gradually changed to a direction which is approximately orthogonal to the fan axis and which is directed to the outside in the fan radial direction DRr. As a result, for example, the pressure loss caused by the outside air blown out from the centrifugal fan 12 as indicated by the arrow F2o hitting the partition plate 15 can be reduced.

Although this embodiment is a modification of the first embodiment, this embodiment can be combined with any of the second to fourth embodiments described above.

(Sixth embodiment)

Next, a sixth embodiment will be described. In this embodiment, points different from the first embodiment described above will be mainly described.

As shown in fig. 10, in a vertical cross section of the blower 10, the partition plate 15 is formed so that an angle formed between the partition plate 15 and the fan axis CL gradually approaches an angle orthogonal to the fan axis CL as going from the partition plate inner end 152 toward the outside in the fan radial direction DRr. In this regard, the present embodiment is the same as the first embodiment.

However, the meandering portion of the partition plate 15 is meandering with respect to one portion shown in fig. 2 in the first embodiment, and two portions shown in fig. 10 in the present embodiment. That is, the partition plate 15 of the present embodiment has meandering portions P1, P2.

Therefore, in the present embodiment, as shown in fig. 10, the partition plate 15 has, in addition to the partition plate outside portion 153 and the partition plate inside portion 154, a partition plate intermediate portion 155 provided between the partition plate outside portion 153 and the partition plate inside portion 154. The partition plate intermediate portion 155 is connected to the partition plate outer portion 153 at a meandering portion P1, and is connected to the partition plate inner portion 154 at a meandering portion P2.

The partition plate intermediate portion 155 is included in a portion located on the other side of the fan axial direction DRa with respect to the partition plate inner side end 152.

(Seventh embodiment)

Next, a seventh embodiment will be described. In this embodiment, points different from the third embodiment described above will be mainly described.

As shown in fig. 11, in the present embodiment, the separation plate 13 has a curved shape in a vertical section of the blower 10. In this regard, the present embodiment is the same as the third embodiment. However, in the present embodiment, the separation plate 13 is not bent over the entire width of the fan radial direction DRr in the vertical section of the blower 10. In this regard, the present embodiment is different from the third embodiment.

Specifically, as shown in fig. 11, in a vertical cross section of the blower 10, the separation plate 13 includes two linear portions 13a and 13b extending linearly, and a curved portion 13c provided between the two linear portions 13a and 13b and curved. The straight portions 13a and 13b of the two portions are continuously connected via the curved portion 13c.

(Eighth embodiment)

Next, an eighth embodiment will be described. In this embodiment, a point different from the fourth embodiment described above will be mainly described.

In the fourth embodiment, as shown in fig. 8, in a vertical section of the blower 10, the separation plate 13 is formed so that the angle between the separation plate 13 and the fan axis CL becomes closer to an angle orthogonal to the fan axis CL stepwise as it goes from the separation plate inner end 132 toward the separation plate outer end 131. In contrast, the separation plate 13 of the present embodiment shown in fig. 12 is not formed in this way.

Specifically, as shown in fig. 12, the separation plate 13 of the present embodiment, like the separation plate 13 of the first embodiment, linearly extends from the separation plate inner end 132 to the separation plate outer end 131 in the vertical section of the blower 10.

The present embodiment is the same as the fourth embodiment except for the above description. In the present embodiment, the same effects as those obtained by the configuration common to the fourth embodiment described above can be obtained as in the fourth embodiment.

(Ninth embodiment)

Next, a ninth embodiment will be described. In this embodiment, points different from the first embodiment described above will be mainly described.

As shown in fig. 13, in the present embodiment, a partition plate 15 is different from the first embodiment.

Specifically, the partition plate inner portion 154 extends so as to be located on the other side of the fan axial direction DRa as it is located on the outer side of the fan radial direction DRr. In this regard, the partition plate 15 of the present embodiment is the same as the partition plate 15 of the first embodiment.

However, unlike the first embodiment, the partition plate outer portion 153 extends so as to be located on one side in the fan axial direction DRa as it is located outward in the fan radial direction DRr. Accordingly, the partition plate 15 has a boundary portion 156 of the partition plate outer side portion 153 and the partition plate inner side portion 154, and the boundary portion 156 is the portion of the partition plate 15 that is the most on the other side in the fan axial direction DRa. Of course, this boundary portion 156 is included in a portion on the other side of the fan axial direction DRa with respect to the partition plate inner side end 152.

Although the present embodiment is based on the modification of the first embodiment, the present embodiment may be combined with any of the second to eighth embodiments described above.

(Tenth embodiment)

Next, a tenth embodiment will be described. In this embodiment, points different from the first embodiment described above will be mainly described.

As shown in fig. 14, in the present embodiment, the orientation of the main board guide surface 122a is different from that of the first embodiment.

Specifically, in the vertical cross section of the blower 10 shown in fig. 14, an intersection point Pn at which the normal Ln of the inner surface 182 of the separation cylinder at the separation cylinder other end position PTa intersects with the main plate guide surface 122a is set as a main plate guide surface intersection point Pn. In this case, in the vertical cross section of the blower 10, the tangential direction D2t of the main plate guide surface 122a obtained at the main plate guide surface intersection point Pn is oriented closer to the direction orthogonal to the fan axis CL than the tangential direction D1t of the separation cylinder inner surface 182 obtained at the separation cylinder other end position PTa.

As a result, in the present embodiment, as in the first embodiment, the rate of change in the flow path cross-sectional area of the flow path formed between the separation cylinder inner surface 182 and the main plate guide surface 122a and through which the inner air flows can be reduced. For the sake of convenience of observation, fig. 14 shows a two-dot chain line L1t passing through the main plate guide surface intersection point Pn so as to be parallel to the tangential direction D1t of the separation cylinder inner surface 182.

Although this embodiment is a modification of the first embodiment, this embodiment can be combined with any of the second to ninth embodiments described above.

(Eleventh embodiment)

Next, an eleventh embodiment will be described. In the present embodiment, although points different from the first embodiment described above will be mainly described, the same points as those of the first embodiment will be described first.

As shown in fig. 15 and 16, the plurality of blades 121 have a blade-side portion 121c and a blade-side portion 121d, respectively, as in the first embodiment. In the description of the present embodiment, the blade-side portion 121c is also referred to as one-side blade 121c, and the blade-side portion 121d is also referred to as the other-side blade 121d.

In addition, as in the first embodiment, the suction port 14a includes a cylinder outside suction port 14b formed outside the fan radial direction DRr with respect to the one side portion 183 of the separation cylinder 18, and a cylinder inside suction port 14c formed inside the fan radial direction DRr with respect to the one side portion 183. The cylinder outside suction port 14b is an annular opening formed around the outer periphery of the cylinder inside suction port 14c.

In addition, as in the first embodiment, each of the plurality of side blades 121c has a side blade leading edge 121e located at an end of the upstream side of the air flow between the plurality of side blades 121 c. The plurality of side blades 121c each have a side blade trailing edge 121f positioned at an end of the downstream side of the air flow between the plurality of side blades 121 c. That is, the one-side blade leading edge 121e forms part of the inlet of the air passage formed between the one-side blades 121c, and the one-side blade trailing edge 121f forms part of the outlet of the air passage.

Similarly, the plurality of other side blades 121d each have the other side blade leading edge 121g located at the upstream end of the air flow between the plurality of other side blades 121 d. The plurality of other side blades 121d each have an other side blade trailing edge 121h positioned at a downstream end of the air flow between the plurality of other side blades 121 d. That is, the other-side blade leading edge 121g forms part of the inlet of the air passage formed between the other-side blades 121d, and the other-side blade trailing edge 121h forms part of the outlet of the air passage.

In addition, as in the first embodiment, the inner diameter DIb of the plurality of other side blades 121d centered on the fan axis CL is smaller than the inner diameter DIa of the plurality of one side blades 121c centered on the fan axis CL. Specifically, the inner diameter DIb of the other side blade 121d is a diameter of a virtual cylindrical surface centered on the fan axis CL and contacting the plurality of other side blades 121d inward in the radial direction. In other words, the inner diameter DIb of the other side blade 121d is a diameter of a virtual cylindrical surface centered on the fan axis CL and inscribed in the plurality of other side blades 121 d. The same description can be made also for the inner diameter dimension DIa of the one-side blade 121 c.

Although this embodiment has the same configuration as the first embodiment, the shape of the vane 121 and the shape of the separation plate 13 in this embodiment are different from those in the first embodiment.

Specifically, the outer diameter DOa of the plurality of one-side blades 121c centered on the fan axis CL is smaller than the outer diameter DOb of the plurality of other-side blades 121d centered on the fan axis CL. Specifically, the outer diameter DOb of the other side blade 121d is a diameter of a virtual cylindrical surface centered on the fan axis CL and contacting the plurality of other side blades 121d radially outward. In other words, the outer diameter DOb of the other side blade 121d is a diameter of a virtual cylindrical surface which is centered on the fan axis CL and circumscribes the plurality of other side blades 121 d. The same can be said for the outer diameter dimension DOa of the one-side blade 121 c.

From the difference between the inside diameter dimensions DIb and DIa and the difference between the outside diameter dimensions DOb and DOa, it can be determined that the blade length LRb of the plurality of other side blades 121d in the fan radial direction DRr is longer than the blade length LRa of the plurality of one side blades 121c in the fan radial direction DRr. In detail, the blade length LRa of the one side blade 121c refers to the radial width occupied by the one side blade 121c in the fan radial direction DRr, and the blade length LRb of the other side blade 121d refers to the radial width occupied by the other side blade 121d in the fan radial direction DRr. Therefore, as shown in fig. 15 and 16, the blade length LRa of the one-side blade 121c can be obtained by the expression "lra= (DOa-DIa)/2". In addition, the blade length LRb of the other side blade 121d can be obtained by the expression of "lrb= (DOb-DIb)/2".

In addition, as shown in fig. 16, in the fan axial direction DRa, the height HFb of the other-side blade leading edge 121g is smaller than the height HFa of the one-side blade leading edge 121 e. Meanwhile, in the fan axial direction DRa, the height HBb of the other-side blade trailing edge 121h is smaller than the height HBa of the one-side blade trailing edge 121 f. In short, the other side blade 121d has a blade shape longer in the fan radial direction DRr and shorter in the fan axial direction DRa than the one side blade 121 c. For example, the blade type of the one side blade 121c of the present embodiment is the blade type of a sirocco fan, and the blade type of the other side blade 121d is the blade type of a turbofan.

In addition, the separation plate 13 extends inward of the fan radial direction DRr than the one-side blade 121 c. Meanwhile, the separation plate 13 extends to the outside of the fan radial direction DRr than the one-side blade 121 c.

As shown in fig. 15 and 16, according to the present embodiment, each of the plurality of blades 121 includes one blade 121c and the other blade 121d. The one-side vane 121c is a portion of one side of the vane 121 with respect to the fan axial direction DRa of the separation plate 13, and the other-side vane 121d is a portion of the other side of the vane 121 with respect to the fan axial direction DRa of the separation plate 13. The separation plate 13 extends inward in the fan radial direction DRr than the one-side blade 121 c. In this way, compared with the case where the separation plate 13 is not configured as such, the space between the separation tube 18 and the one-side blade 121c can be enlarged in the fan radial direction DRr without enlarging the gap between the separation tube 18 and the separation plate 13. Therefore, the pressure loss caused by the air sucked between the blades 121c on the one side by the radially outer side of the separation tube 18 can be reduced.

In addition, according to the present embodiment, the inner diameter dimension DIb of the plurality of other side blades 121d centered on the fan axis CL is smaller than the inner diameter dimension DIa of the plurality of one side blades 121c centered on the fan axis CL. Therefore, compared with the case where the magnitude relation between the inner diameter dimensions DIa, DIb is not the same, the suction flow path area is easily obtained on the inner side in the radial direction with respect to the one-side blade 121c, and the pressure loss caused by the air sucked into the centrifugal fan 12 can be reduced.

In addition, according to the present embodiment, the inner diameter dimension DIb of the other side blade 121d is smaller than the inner diameter dimension DIa of the one side blade 121c, and the blade length LRb of the other side blade 121d is longer than the blade length LRa of the one side blade 121 c. This makes it possible to reduce the impeller height (in other words, the fan height) which is the height of the centrifugal fan 12 in the fan axial direction DRa without any disadvantage.

(Other embodiments)

(1) In the first to tenth embodiments described above, the separator bowl end surface 185a is a surface parallel to the fan axial direction DRa, for example, as shown in fig. 2, but may be a surface inclined with respect to the fan axial direction DRa. The outer end surface 131a of the pair of separation plates 13, the inner end surface 132a of the separation plate 13, and the partition plate end surface 152a are also the same.

(2) In the first to tenth embodiments described above, the width of the separation plate 13 in the fan radial direction DRr is the same as the width of the blade 121, for example, as shown in fig. 1, but the present invention is not limited thereto. For example, the separating plate 13 may extend outward or inward in the fan radial direction DRr with respect to the blade 121. In addition, the width of the separation plate 13 may be narrower than the width of the blades 121 in the fan radial direction DRr.

(3) In the above embodiments, the centrifugal fan 10 is applied to the vehicle air conditioner having the two-layer flow of the inside and outside air, but the application of the centrifugal fan 10 is not limited thereto. For example, the centrifugal fan 10 may be used for applications other than the vehicle air conditioner.

(4) In the above embodiments, for example, as shown in fig. 1, the plate thickness of the partition plate 15, the plate thickness of the separation plate 13, and the plate thickness of the separation tube 18 are the same or substantially the same, but may be different from each other.

(5) In the first to tenth embodiments described above, for example, as shown in fig. 1, the air passage forming portion 142 and the partition plate 15 are formed as an integrally molded product formed of an integral resin, but this is only an example. The air passage forming portion 142 and the partition plate 15 may be formed as separate members, and the fan housing 14 may be configured by assembling the air passage forming portion 142 and the partition plate 15. The air passage forming portion 142 may be formed of a plurality of members formed separately. The same is true for the partition plate 15.

(6) In the first to tenth embodiments described above, for example, as shown in fig. 1, the blade type of the blade 121, the blade-side portion 121c, and the blade-side portion 121d are all blade types of the sirocco fan, but are not limited thereto.

For example, the blade type of the blade-side portion 121c may be a blade type of a sirocco fan, and the blade type of the blade-side portion 121d may be a blade type of a radial fan. Conversely, the blade type of the blade-side portion 121c may be a radial fan blade type, and the blade type of the blade-side portion 121d may be a sirocco fan blade type. The blade type of the blade-side portion 121c may be a blade type of a sirocco fan, and the blade type of the blade-side portion 121d may be a blade type of a turbofan. Conversely, the blade type of the blade-side portion 121c may be a blade type of a turbo fan, and the blade type of the blade-side portion 121d may be a blade type of a sirocco fan. In addition, both the blade type of the blade-side portion 121c and the blade type of the blade-side portion 121d may be the blade type of the radial fan. In addition, both the blade type of the blade-side portion 121c and the blade type of the blade-side portion 121d may be blade types of the turbofan. In short, the blade type of the blade-side portion 121c and the blade type of the blade-side portion 121d may be the same as each other or may be different from each other. Further, the number of the blade-side portions 121c and the number of the blade-side portions 121d may be the same or different from each other.

(7) In the first embodiment described above, as shown in fig. 2, although the extending direction of the separation plate 13 at the position of the separation plate inner end 132 and the extending direction of the separation tube 18 at the position of the separation tube other end 185 are different from each other in the longitudinal section of the blower 10, this is just an example. For example, it is also conceivable that the extending directions of the both are different from each other. The same applies to the embodiments following the second embodiment.

In addition, although the extending direction of the separation plate 13 at the position of the separation plate outer end 131 and the extending direction of the separation plate 15 at the position of the separation plate inner end 152 are the same as each other, this is also just one example. For example, it is also conceivable that the extending directions of the both are different from each other. The same applies to the embodiments following the second embodiment. The above extending directions of the separation plate 13, the separation plate 15, and the separation tube 18 can be interpreted as gradients with respect to a predetermined reference (for example, the fan axis CL).

(8) In the above embodiments, for example, as shown in fig. 1, the other side portion of the leading edge of the blade 121 with respect to the fan axial direction DRa of the separation plate 13 is inclined with respect to the fan axial center CL, but the shape of the leading edge of the blade 121 is not limited. For example, the leading edge of the vane 121 may extend from one end 121a to the other end 121b along the fan axis CL. In addition, a portion of the leading edge of the vane 121 on the side of the fan axis direction DRa of the separation plate 13 may be inclined with respect to the fan axis CL.

(9) The present invention is not limited to the above-described embodiments, and various modifications can be made. The above embodiments are not independent of each other, and can be appropriately combined except for the case where the combination is clearly impossible.

In the above embodiments, the elements constituting the embodiments are not necessarily required, except when they are particularly clearly required or when they are clearly considered to be required in principle, or the like. In the above embodiments, the numbers, values, amounts, ranges, and the like of the constituent elements of the embodiments are not limited to a specific number except for the case where they are particularly clearly indicated and the case where they are obviously limited to the specific number in principle.

In the above embodiments, when materials, shapes, positional relationships, and the like of the constituent elements and the like are mentioned, the materials, shapes, positional relationships, and the like are not limited to those described above, except for the cases where they are specifically shown and where they are limited to specific materials, shapes, positional relationships, and the like in principle.

(Summary)

According to a first aspect showing some or all of the above embodiments, the centrifugal fan includes a centrifugal fan that blows out air sucked from one side in an axial direction of a fan axial center toward an outside in a radial direction, a fan housing, and a separation tube. The separation tube is formed to extend in the radial direction of the centrifugal fan as it extends to the other side in the axial direction, and is formed to have a shape inclined with respect to the axial direction and extending outward in the radial direction at the other end position of the separation tube, which is the position of the other end of the separation tube in the axial direction.

In addition, according to the second aspect, the separation plate has a separation plate outer end provided on the outer side in the radial direction and a separation plate inner end provided on the inner side in the radial direction. The inner end of the separator is located on the one side in the axial direction with respect to the outer end of the separator. Therefore, the pressure loss caused by the outside air flowing along the separation cylinder and having the velocity component directed to the other side in the axial direction hitting the separation plate can be reduced.

In addition, according to the third aspect, in a vertical section of the centrifugal fan cut in a plane including the fan axis, the separation plate is curved so as to expand in the radial direction at an angle closer to an orientation orthogonal to the fan axis as it goes from the inner end of the separation plate toward the outer end of the separation plate. Therefore, the pressure loss caused by the outside air flowing along the separation cylinder and having the velocity component directed to the other side in the axial direction hitting the separation plate can be reduced. Further, by making the outside air follow the separation plate, the velocity component of the outside air toward the other side in the axial direction can be reduced, and the outside air can be guided outward in the radial direction.

In addition, according to the fourth aspect, in a vertical section of the centrifugal fan cut in a plane including the fan axis, the angle formed by the separation plate and the fan axis gradually approaches an angle orthogonal to the fan axis as the separation plate moves from the inner end of the separation plate toward the outer end of the separation plate. In this way, the same operational effects as those of the third aspect described above can be obtained.

In addition, according to a fifth aspect, the partition plate has a partition plate inner end provided on the inner side in the radial direction and a portion located on the other side in the axial direction with respect to the partition plate inner end. Therefore, it is difficult to prevent the air blown out from the plurality of blades from flowing radially outward while being inclined with respect to the axial direction while having a velocity component directed to the other side in the axial direction around the inner end of the partition plate. Therefore, the pressure loss caused by the outside air blown out from between the blades hitting the partition plate can be reduced.

In addition, according to a sixth aspect, the fan case has an outer peripheral wall facing the blown-out air passage from the radial outer side. The partition plate has a partition plate outer end provided on the outer side in the radial direction and connected to the outer peripheral wall, and the partition plate has a shape that expands in a direction orthogonal to the axial direction at a position of the partition plate outer end. Therefore, compared with a case where the partition plate is inclined at the position of the outer end of the partition plate, faces the other side in the axial direction, and expands radially outward, for example, the direction of the outside air reaching the outer peripheral wall of the fan case along the partition plate can be suppressed from rapidly changing. As a result, the output of the centrifugal fan can be further improved.

In addition, according to the seventh aspect, in a vertical section of the centrifugal fan cut in a plane including the fan axis, the partition plate is curved so as to expand in the radial direction at an angle approaching an orientation orthogonal to the fan axis as it goes from the inner end of the partition plate to the outer side in the radial direction. Therefore, the direction of the air flowing along the partition plate can be gradually changed to a direction orthogonal to the fan axis and close to the outward direction in the radial direction. As a result, for example, the pressure loss caused by the outside air blown out from the centrifugal fan hitting the partition plate can be reduced.

In addition, according to the eighth aspect, in a vertical section of the centrifugal fan cut in a plane including the fan axis, the partition plate is formed so as to approach an angle orthogonal to the fan axis stepwise as it goes from the inner end of the partition plate toward the outer side in the radial direction. In this way, the same operational effects as those of the seventh aspect described above can be obtained.

In addition, according to a ninth aspect, the separation plate has an inner end surface extending from one side to the other side in the axial direction at a position of the inner end in the radial direction. The separation cylinder has a separation cylinder end surface extending from one side to the other side in the axial direction at the other end position of the separation cylinder. In the axial direction, the other end of the inner end face is located on the other side than the one end of the separator tube end face. Therefore, compared with a case where the end of the one side of the separation cylinder end surface is located on one side as opposed to the end of the other side of the inner end surface, it is possible to suppress mixing of the two air streams separated by the separation cylinder through the gap between the separation cylinder and the separation plate.

In addition, according to a tenth aspect, the separation plate has an outer end surface extending from one side to the other side in the axial direction at a position of the outer end in the radial direction. The partition plate has a partition plate end surface extending from one side to the other side in the axial direction at a position of the radially inner end. In the axial direction, the end on one side of the outer end face is located on one side of the other end of the partition plate end face. Therefore, compared with a case where the end of the outer end face on the other side is located on the other side than the end of the other side of the partition plate end face, the two air flows separated by the separation plate can be suppressed from being mixed through the gap between the partition plate and the separation plate.

In addition, according to an eleventh aspect, the centrifugal fan has a main plate which is disposed on the other side in the axial direction with respect to the separation tube, and has a plate shape extending in the radial direction. The main plate has a main plate guide surface on one side in the axial direction, and the main plate guide surface guides the inside air so that the inside air flows outward in the radial direction. The separation cylinder has a separation cylinder inner surface extending to the other end position of the separation cylinder, and the separation cylinder inner surface includes an inward surface facing the inside in the radial direction. The main plate guide surface extends so as to be located on the other side in the axial direction as it is located on the outer side in the radial direction. In a vertical section of the centrifugal fan cut through a plane including the fan axis, a tangential direction of the main plate guide surface obtained at an intersection point of a normal line of the inner side surface of the separation cylinder at the other end position of the separation cylinder and the main plate guide surface is oriented in the same direction as a tangential direction of the inner side surface of the separation cylinder obtained at the other end position of the separation cylinder. Alternatively, in the vertical cross section, the tangential direction of the main plate guide surface is a direction closer to a direction orthogonal to the fan axis than the tangential direction of the inner surface of the separation cylinder.

Here, in the flow path formed between the inner surface of the separation tube and the main plate guide surface and through which the inside air flows, the circumferential length of the flow path cross section centered on the fan axis increases toward the downstream side, and therefore, the change in the circumferential length acts to expand the flow path cross section toward the downstream side. Further, it is assumed that the change in the height of the flow path cross section indicated by the vertical section contributes to the expansion of the flow path cross section when the tangential direction of the inner surface of the separation tube is a direction closer to the direction orthogonal to the fan axis than the tangential direction of the main plate guide surface.

In contrast, in the eleventh aspect, the change in the height of the flow path cross section indicated by the vertical cross section contributes to the expansion of the flow path cross section. Therefore, the rate of change in the flow path cross-sectional area of the flow path through which the inside air flows can be reduced as compared with the virtual case described above.

In addition, according to a twelfth aspect, each of the plurality of blades includes: a blade-side portion which is a portion of the blade on one side in the axial direction with respect to the separation plate; and a blade other side portion which is a portion of the blade on the other side with respect to the above-described axial direction of the separation plate. And the separating plate extends to the inside in the radial direction than the blade-side portion. In this way, the space between the blade-side portion and the separation cylinder can be enlarged in the radial direction without enlarging the gap between the separation cylinder and the separation plate, as compared with the case where the separation plate is not of such a structure. Therefore, the pressure loss caused by the air sucked into the vane-side portions through the radially outer side of the separation cylinder can be reduced.

In addition, according to the thirteenth aspect, the inner diameter dimension of the other side portion of the blade centered on the fan axis is smaller than the inner diameter dimension of the one side portion of the blade centered on the fan axis. Therefore, the suction flow path area is easily acquired radially inward of the blade-side portion, and the pressure loss caused by the air sucked into the centrifugal fan can be reduced.

Claims

1. A centrifugal blower is characterized by comprising:

A centrifugal fan (12) which has a plurality of blades (121) and a separation plate (13) arranged around a fan axis (CL) and blows out air sucked from one side in an axial direction (DRa) of the fan axis toward the outside in a radial direction (DRr);

A fan housing (14) that houses the centrifugal fan and that is formed with a suction port (14 a) that is arranged on the one side in the axial direction with respect to the centrifugal fan and through which air sucked into the centrifugal fan passes, and a blowout air passage (142 a) that is arranged on the outer side in the radial direction with respect to the centrifugal fan and through which air blown from the centrifugal fan flows, the fan housing having a partition plate (15) that partitions the blowout air passage into a first air passage (142 b) and a second air passage (142 c) that is arranged on the other side in the axial direction with respect to the first air passage; and

A separation tube (18) which is disposed on the inner side of the centrifugal fan in the radial direction with respect to the plurality of blades and has a tubular shape facing the axial direction,

The separation cylinder separates air passing through the suction port into inside air flowing inside in the radial direction with respect to the separation cylinder and outside air flowing outside in the radial direction with respect to the separation cylinder,

The separation plate is in a plate shape expanding in the radial direction and configured such that, between the plurality of blades, the outside air flows on the one side with respect to the axial direction of the separation plate, and the inside air flows on the other side with respect to the axial direction of the separation plate,

The partition plate is configured such that the outside air flows from the centrifugal fan into the first air passage, and the inside air flows from the centrifugal fan into the second air passage,

The separation cylinder expands in the radial direction as it moves toward the other side in the axial direction, and is formed in a shape inclined with respect to the axial direction and expanding toward the outside in the radial direction at a separation cylinder other end position (PTa) which is a position of an end of the other side in the axial direction of the separation cylinder,

The plurality of blades each include: a blade-side portion (121 c) that is a portion of the blade on the side with respect to the axial direction of the separation plate; and a blade other side portion (121 d) which is a portion of the other side of the blade with respect to the axial direction of the separation plate,

A blade length (LRb) of the blade-side portion (121 d) in the radial direction is longer than a blade length (LRa) of the blade-side portion (121 c) in the radial direction.

2. A centrifugal blower according to claim 1, wherein,

The separating plate has a separating plate outer end (131) arranged on the outer side in the radial direction and a separating plate inner end (132) arranged on the inner side in the radial direction,

The separator plate inner end is located on the one side of the axial direction with respect to the separator plate outer end.

3. A centrifugal blower according to claim 2, wherein,

In a vertical section of the centrifugal fan taken in a plane including the fan axis, the separation plate is curved so as to expand in the radial direction at an angle closer to an orientation orthogonal to the fan axis as it goes from the inner end of the separation plate toward the outer end of the separation plate.

4. A centrifugal blower according to claim 2, wherein,

In a vertical section of the centrifugal fan taken in a plane including the fan axis, the angle formed by the separation plate and the fan axis gradually approaches an angle orthogonal to the fan axis as the separation plate moves from the inner end of the separation plate toward the outer end of the separation plate.

5. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

The partition plate has a partition plate inner end (152) provided on the inner side in the radial direction and portions (153, 155, 156) located on the other side in the axial direction with respect to the partition plate inner end.

6. The centrifugal blower according to claim 5, wherein,

The fan housing has an outer peripheral wall (143) facing the blown-out air passage from the radially outer side,

The partition plate has a partition plate outer end (151) provided on the outer side in the radial direction and connected to the outer peripheral wall, and the partition plate has a shape that expands in a direction orthogonal to the axial direction at a position of the partition plate outer end.

7. The centrifugal blower according to claim 5, wherein,

In a vertical section of the centrifugal fan taken in a plane including the fan axis, the partition plate is curved so as to expand in the radial direction at an angle closer to an orientation orthogonal to the fan axis as it goes from an inner end of the partition plate toward the outer side in the radial direction.

8. The centrifugal blower according to claim 5, wherein,

In a vertical section of the centrifugal fan taken in a plane including the fan axis, the partition plate is formed so that an angle formed between the partition plate and the fan axis becomes closer to an angle orthogonal to the fan axis stepwise as it goes from an inner end of the partition plate to an outer side in the radial direction.

9. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

The separating plate has an inner end surface (132 a) extending from the one side to the other side in the axial direction at a position of the radially inner end,

The separator has a separator end surface (185 a) extending from the one side to the other side in the axial direction at the other end position of the separator,

In the axial direction, the other side end (132 b) of the inner end surface is located on the other side than the one side end (185 b) of the separator tube end surface.

10. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

The separating plate has an outer end surface (131 a) extending from the one side to the other side in the axial direction at a position of the radially outer end,

The partition plate has a partition plate end face (152 a) extending from the one side to the other side of the axial direction at a position of the radially inner end,

In the axial direction, the one end (131 b) of the outer end face is located on the one side than the other end (152 b) of the partition plate end face.

11. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

The centrifugal fan has a main plate (122) which is disposed on the other side in the axial direction with respect to the separation cylinder and which has a plate shape extending in the radial direction,

The main plate has a main plate guide surface (122 a) on the one side in the axial direction, the main plate guide surface guiding the inside air so that the inside air flows toward the outside in the radial direction,

The separation cylinder has a separation cylinder inner side (182) extending to the other end position of the separation cylinder, the separation cylinder inner side including an inward-facing surface (182 a) facing the inner side in the radial direction,

The main plate guide surface extends so as to be located on the other side in the axial direction as it is located on the outer side in the radial direction,

In a vertical section of the centrifugal fan taken in a plane including the fan axial center, a tangential direction (D2 t) of the main plate guide surface obtained at an intersection point (Pn) of a normal line (Ln) of the inner side surface of the separation cylinder at the other end position of the separation cylinder and the main plate guide surface is the same direction as a tangential direction (D1 t) of the inner side surface of the separation cylinder obtained at the other end position of the separation cylinder, or is a direction closer to a direction orthogonal to the fan axial center than the tangential direction of the inner side surface of the separation cylinder.

12. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

The separation plate extends to the radially inner side than the blade-side portion.

13. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

An inner diameter dimension (DIb) of the other side portion of the blade centered on the fan axis is smaller than an inner diameter dimension (DIa) of the one side portion of the blade centered on the fan axis.

14. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

An outer diameter dimension (DOa) of the blade-side portion (121 c) centered on the fan axis is smaller than an outer diameter dimension (DOb) of the blade-side portion (121 d) centered on the fan axis.

15. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

The separating tube (18) is configured as a different component with respect to the centrifugal fan (12), and the separating tube (18) is a non-rotating component that does not rotate.

16. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

The number of the blade-side portions (121 d) is different from the number of the blade-side portions (121 c).

17. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

A plurality of the blade-other-side portions (121 d) having other-side blade trailing edges (121 h) at ends of downstream sides of air flows between the plurality of blade-other-side portions,

A plurality of the blade-side portions (121 c) having one-side blade trailing edges (121 f) at ends of downstream sides of air flows between the plurality of blade-side portions,

In the axial direction, the height (HBb) of the other side blade trailing edge (121 h) is smaller than the height (HBa) of the one side blade trailing edge (121 f).

18. A centrifugal blower as set forth in any one of claims 1 to 4, wherein,

A plurality of the blade-other-side portions (121 d) having other-side blade leading edges (121 g) at ends of the upstream sides of the air flows between the plurality of blade-other-side portions,

A plurality of the blade-side portions (121 c) having one-side blade leading edges (121 e) at ends of upstream sides of air flows between the plurality of blade-side portions,

In the axial direction, the height (HFb) of the other side blade leading edge (121 g) is smaller than the height (HFa) of the one side blade leading edge (121 e).