WO2015059884A1

WO2015059884A1 - Centrifugal air blower and air-conditioning device

Info

Publication number: WO2015059884A1
Application number: PCT/JP2014/005138
Authority: WO
Inventors: 生田　晴樹; 伊藤　公一; 伊藤　功治
Original assignee: 株式会社デンソー
Priority date: 2013-10-25
Filing date: 2014-10-09
Publication date: 2015-04-30
Also published as: JP2015083777A

Abstract

The disclosed centrifugal air blower is equipped with: a turbo fan (12) having multiple blades (121); and a casing (14) for housing the turbo fan (12). An outer section of the casing (14) in the radial direction of the turbo fan (12) forms a fluid path (22) for a fluid blown out from the turbo fan (12) to flow therein. A blowout port (23) for blowing out the fluid flowing in the fluid path (22) is formed at an end of the casing (14) in the radial direction of the turbo fan (12). The size (W1) of the section of the fluid path (22) between the turbo fan (12) and the blowout port (23) is greater than the diameter (d1) of the turbo fan (12). The fluid path (22) has an expanded section (28) that is expanded beyond the turbo fan (12) in the axial direction thereof at least on one side in the axial direction. The expanded section (28) is a space where the air blown out from the turbo fan (12) swirls.

Description

Centrifugal blower and air conditioner

Cross-reference of related applications

This application is based on Japanese Patent Application No. 2013-221712 filed on Oct. 25, 2013, the disclosure of which was incorporated into this application by reference.

The present disclosure relates to a centrifugal blower that blows air by rotation of a turbo fan, and an air conditioner including the centrifugal blower.

Conventionally, Patent Document 1 describes a so-called plug fan. The plug fan is a type of centrifugal blower, and is a blower in which a turbo fan is arranged in a casing and blows air in one direction. The plug fan is a scrollless blower that does not have a spiral (logarithmic spiral) casing (scroll casing), and the casing has a substantially rectangular shape.

The turbo fan is a fan having blades (blades) opposite to the rotation direction. In general, a turbofan is characterized by higher fan efficiency but less airflow than a sirocco fan whose blades are directed in the direction of rotation.

Scroll fans with scroll casings are difficult to design and manufacture because it is necessary to design and manufacture scroll casings with complex shapes. On the other hand, since the plug fan does not have a scroll casing having a complicated shape, it is easier to design and manufacture than a scroll fan.

On the other hand, a scroll blower provided with a scroll casing is widely applied to a blower of an air conditioner. In this type of air conditioner, for example, air blown from a scroll blower is heat-exchanged by a heat exchanger.

JP 2012-177363 A

However, in the above prior art (plug fan), since the air blown radially outward from the turbo fan collides with the side wall of the casing and then flows backward without interfering with the other blown air, the fan efficiency May be lowered.

On the other hand, when the scroll blower is applied to a blower of an air conditioner, since the nose is formed in the scroll casing, the distance between the sirocco fan and the heat exchanger can be shortened to reduce the size of the air conditioner. May be difficult.

Further, when the scroll blower is applied to a blower of an air conditioner, the flow of air blown from the sirocco fan into the air passage in the scroll casing is greatly disturbed between the nose of the scroll casing and the outlet (vortex is generated). ). Therefore, a wind speed distribution is generated in the heat exchanger. As a result, a temperature distribution may occur in the air heat-exchanged by the heat exchanger, and the air conditioning feeling may be impaired.

This indication aims at providing the centrifugal air blower which can improve the fan efficiency of the centrifugal air blower which does not have a scroll casing in view of the above-mentioned point.

Furthermore, in view of the above points, it is an object of the present disclosure to provide an air conditioner that can be downsized and can suppress the wind speed distribution in the heat exchanger.

The centrifugal blower of the present disclosure includes a turbo fan having a plurality of blades and a casing that houses the turbo fan.

The outer portion of the casing in the radial direction of the turbofan forms a fluid passage through which the fluid blown out from the turbofan flows. A blower outlet that blows out the fluid that has flowed through the fluid passage is formed at the end of the casing in the radial direction of the turbofan. A dimension of a portion of the fluid passage between the turbo fan and the outlet is larger than the diameter of the turbo fan. The fluid passage has an enlarged portion that extends in the axial direction on at least one side of the axial direction of the turbofan. The enlarged portion is a space in which the fluid blown out from the turbofan swirls.

According to this, since the fluid blown out from the turbo fan swirls in the enlarged portion, the back flow of the fluid blown out from the turbo fan is suppressed, and interference with other blown winds can be suppressed. Therefore, fan efficiency can be improved.

The air conditioner of the present disclosure includes a blower that blows air and a heat exchanger that exchanges heat between the air blown by the blower.

The blower is a centrifugal blower having a turbo fan including a plurality of blades and a casing for storing the turbo fan. A radially outer portion of the turbofan in the casing forms a fluid passage through which the fluid blown out from the turbofan flows. A blower outlet that blows out the fluid that has flowed through the fluid passage is formed at the end of the casing in the radial direction of the turbofan. The size of the portion of the fluid passage between the turbofan and the outlet is larger than the diameter of the turbofan. A heat exchanger is arranged at the outlet.

According to this, since the air blower of the air conditioner is composed of a centrifugal blower that does not have a scroll casing, the size of the air conditioner can be reduced, and the wind speed distribution in the heat exchanger can be suppressed. Moreover, since there is no scroll casing, design and manufacture can be facilitated.

It is a top view which shows the indoor air conditioning unit in 1st Embodiment. FIG. 2 is a sectional view taken along the line II-II in FIG. It is sectional drawing which shows the air blower in 1st Embodiment. FIG. 4 is a sectional view taken along line IV-IV in FIG. 3. FIG. 5 is a VV cross-sectional view of FIG. 3. FIG. 6 is a sectional view taken along line VI-VI in FIG. 3. FIG. 4 is a sectional view taken along line VII-VII in FIG. It is sectional drawing which shows the air blower in 2nd Embodiment. It is sectional drawing which shows the air blower in 3rd Embodiment. It is sectional drawing which shows the air blower in 4th Embodiment. It is sectional drawing which shows the air blower in 5th Embodiment. It is sectional drawing which shows the air blower in 6th Embodiment. It is sectional drawing which shows the air blower in 7th Embodiment. It is sectional drawing which shows an air flow in case the distance between a fan and an evaporator is large in the air blower of 8th Embodiment. It is sectional drawing which shows an air flow in case the distance between a fan and an evaporator is small in the air blower of 8th Embodiment. It is a graph which shows the relationship between the distance between a fan and an evaporator, and fan efficiency in the air blower of 8th Embodiment. It is a graph which shows the relationship between the distance between a fan and an evaporator, and the wind speed distribution in an evaporator in the air blower of 8th Embodiment. It is sectional drawing which shows the air blower in 9th Embodiment.

Hereinafter, embodiments will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings. In addition, the up-down (front-back) arrow in a figure has shown the up-down direction (front-back direction) in the vehicle mounting state.
(First embodiment)
The indoor air conditioning unit 10 of the vehicle air conditioner shown in FIGS. 1 and 2 includes a blower 11.

The indoor air-conditioning unit 10 is disposed inside the instrument panel (instrument panel) at the foremost part of the vehicle interior, and constitutes a front-seat air-conditioning unit that mainly blows air-conditioned air toward passengers seated in the front seat of the vehicle is doing.

The blower 11 is a centrifugal blower having a fan 12 (impeller), a motor 13 and a blower casing 14 (casing). The blower 11 is a scrollless blower that does not have a spiral (logarithmic spiral) scroll casing.

The fan 12 is a turbo fan having blades 121 (blades) opposite to the rotation direction. In general, a turbofan has higher fan efficiency but less airflow than a sirocco fan whose blades are oriented in the direction of rotation.

In the example of FIG. 2, the axial direction of the fan 12 is directed in the vertical direction. As shown in parentheses in FIG. 2, the axial direction may face the horizontal direction (in the example of FIG. 12, the front-rear direction of the vehicle).

The fan 12 is a blower having a plurality of blades 121 around the boss portion 122, sucking air from the radially inner side, and blowing the sucked air to the radially outer side. The boss portion 122 is connected to the output shaft 131 of the motor 13. For example, the fan 12 is integrally formed of resin (for example, polypropylene).

The motor 13 is a drive unit that rotationally drives the fan 12 in the direction of the arrow R1 in FIG. 1, and is configured by an electric motor in this embodiment. The motor 13 is fixed to a blower casing 14 that houses the fan 12. The motor 13 is disposed on one end side in the axial direction of the fan 12 (lower end side in FIG. 2).

The blower casing 14 is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.

The blower casing 14 has a semi-oval shape in a planar shape (planar shape shown in FIG. 1) viewed from the axial direction. Specifically, one end side portion (the left end side portion in FIG. 1) in the full length direction of the blower casing 14 has a semicircular shape. The other end side part (the right end side part in FIG. 1) of the full length direction among the blower casings 14 is rectangular.

A suction port 16 for introducing air is formed in one end side of the fan casing 14 in the axial direction of the fan 12 (on the side opposite to the motor 13). A bell mouth is provided at the outer edge of the suction port 16 to smoothly guide the intake air to the fan 12.

The inside / outside air switching box 20 is connected to the suction port 16. The inside / outside air switching box 20 switches and introduces inside air and outside air into the suction port 16. In the inside / outside air switching box 20, an inside air introduction port 201 and an outside air introduction port 202 are formed. The inside / outside air switching box 20 is provided with an inside / outside air switching door 21 that opens and closes the inside air introduction port 201 and the outside air introduction port 202.

An air passage 22 (fluid passage) through which air (fluid) blown out from the fan 12 flows is formed inside the blower casing 14 and outside the fan 12 in the radial direction. An air outlet 23 is formed on the air flow downstream side of the air passage 22. The air outlet 23 blows out the air flowing through the air passage 22 to the outside of the blower 11.

The blower outlet 23 is formed at the end of the blower casing 14 in the radial direction of the fan 12. Specifically, the blower outlet 23 is formed in the end part (right end part in FIG. 1) of the blower casing 14 on the rectangular part side. Therefore, the opening direction (right side in FIG. 1) of the blower outlet 23 is parallel to the full length direction of the blower casing 14.

The air outlet casing 25 is connected to the air outlet 23. The air conditioning casing 25 forms an air passage through which air blown from the blower 11 flows. The air conditioning casing 25 is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent in strength.

An evaporator 26 is disposed at the most upstream part of the air flow of the air conditioning casing 25. In other words, the evaporator 26 is arranged at the outlet 23 of the blower casing 14. The evaporator 26 is a cooling heat exchanger that cools the air by exchanging heat between the low-pressure refrigerant in the refrigeration cycle and the air flowing in the air conditioning casing 25.

An air outlet (not shown) that blows air toward the passenger compartment is formed in the most downstream portion of the air flow of the air conditioning casing 25.

As described above, the blower 11 constitutes a scrollless blower that does not have a spiral (logarithmic spiral) scroll casing. Therefore, as shown in FIG. 3, the dimension W1 (the vertical dimension in FIG. 1) of the portion of the air passage 22 between the fan 12 and the outlet 23 is larger than the diameter d1 of the fan 12. . In the present embodiment, the dimension W1 is a dimension when a portion of the air passage 22 between the fan 12 and the outlet 23 is viewed from the axial direction. In other words, the dimension W 1 is a dimension in the radial direction of a portion of the air passage 22 between the fan 12 and the outlet 23.

The rotation axis A1 of the fan 12 is one side in the direction perpendicular to the axial direction of the blower casing 14 (the lower side in FIG. 3) with respect to the center line CL (virtual line) of the blower casing 14 in the direction perpendicular to the axial direction. Is offset. More specifically, the offset direction of the fan 12 is a direction (downward in FIG. 3) that is shifted from the opening direction of the air outlet 23 by 90 ° in the fan rotation direction R1.

As a result, between the fan 12 and the semicircular portion of the blower casing 14, the radial dimension of the air passage 22 (the dimension measured in the radial direction of the fan 12) increases in the direction of the fan rotation direction R 1. ing.

As shown in FIGS. 3, 4, 5, 6, and 7, the air passage 22 has an enlarged portion 28 that gradually expands in the axial direction from the starting portion 27 toward the fan rotation direction R 1. . More specifically, the expansion portion 28 expands in the direction opposite to the suction port 16 in the axial direction (the lower side in FIGS. 4 to 7).

As shown in FIG. 3, the starting point portion 27 is located in a range B1 between the first virtual line L1 and the second virtual line L2. The first imaginary line L1 is an imaginary line extending from the rotation axis A1 of the fan 12 toward the opening direction of the air outlet 23 (right direction in FIG. 3).

The second virtual line L2 is a virtual line extending from the rotation axis A1 of the fan 12 toward the offset direction of the fan 12 (downward in FIG. 3). In other words, the second virtual line L2 is a virtual line extending from the rotation axis A1 of the fan 12 toward the minimum width portion 22a of the air passage 22. The minimum width portion 22a is a portion of the air passage 22 where the dimension (width) of the air passage 22 is minimized when viewed from the fan axial direction. In other words, the air passage 22 has a minimum width portion 22a that minimizes the dimension of the air passage 22 in the radial direction.

In the example of FIG. 3, the angle formed by the first virtual line L1 and the second virtual line L2 is 90 °. In the example of FIG. 3, the starting point portion 27 is located on an imaginary line that connects the rotation axis A 1 of the fan 12 and the end portion (lower end portion in FIG. 3) on the fan rotation direction R 1 side of the outlet 23.

The expansion of the expansion unit 28 ends at the start point 27. Therefore, the enlarged portion 28 has a step between the starting point portion 27 and the enlarged portion 28.

Next, the operation of this embodiment in the above configuration will be described. When the motor 13 is energized and the fan 12 is rotationally driven, the fan 12 sucks air through the suction port 16 and blows it outward in the radial direction of the fan 12. The air blown out from the fan 12 flows through the air passage 22 toward the air outlet 23 and is blown out from the air outlet 23 to the air conditioning casing 25.

The air blown out from the air outlet 23 to the air conditioning casing 25 is cooled by the evaporator 26 and then blown out from the air outlet (not shown) of the air conditioning casing 25 toward the vehicle interior.

The air passage 22 has an enlarged portion 28 that expands outward in the axial direction in at least one of the axial directions. Specifically, in the present embodiment, the air passage 22 has an enlarged portion 28 that gradually expands downward from the starting point portion 27 toward the fan rotation direction R1. As shown by the arrow in FIG. 2, the air blown from the fan 12 swirls in the enlargement unit 28.

Therefore, as shown by the arrows in FIG. 2, the air blown out from the fan 12 collides with the side wall (wall extending in the axial direction) of the blower casing 14, and then both ends in the axial direction (upper side and lower side in FIG. 2). ) And blown out.

As a result, interference between the air blown from the fan 12 can be reduced, so that fan efficiency can be improved. Furthermore, since the area of the air passage 22 is increased by the amount of the enlarged portion 28 formed, the pressure loss is reduced, and consequently the fan efficiency can be improved.

In particular, when the ratio of the diameter d1 of the fan 12 to the dimension W2 in the axial direction of the blower casing 14 (see FIG. 3) is large (for example, when W2 <1.3 × d1), the fan efficiency improvement effect by the expansion unit 28 Is remarkably obtained.

In the present embodiment, the air passage 22 through which the air blown out from the fan 12 flows has an enlarged portion 28 that extends from the fan 12 toward one side in the axial direction. The enlarged portion 28 is a space in which the air blown from the fan 12 turns.

According to this, since the air blown out from the fan 12 swirls at the enlarged portion 28, the backflow of the air blown out from the fan 12 is suppressed, and interference with other blown winds can be suppressed. Therefore, fan efficiency can be improved.

Moreover, since fan efficiency can be improved without expanding the physique of the blower casing 14 in the radial direction of the fan 12, it is possible to suppress deterioration in mountability on the vehicle.

In the present embodiment, the enlarged portion 28 has a first imaginary line L1 extending from the rotation axis A1 toward the opening direction of the outlet 23, and the first imaginary line L1 is 90 ° in the fan rotation direction R1 with the rotation axis A1 as the center. Starting from a portion 27 (starting portion) located between the rotated second imaginary line L2, it gradually expands toward the rotation axis A1 in the fan rotation direction R1. In other words, the dimension of the enlarged portion 28 in the radial direction is gradually increased toward the fan rotation direction R1.

Furthermore, in the present embodiment, the air passage 22 has a minimum width portion 22a at a position shifted from the starting point portion 27 by 90 ° in the rotation direction R1. The dimension of the air passage 22 in the radial direction is minimum at the minimum width portion 22a. The enlarged portion 28 rotates at the fan starting from a portion 27 (starting portion) located between the minimum width portion 22a of the air passage 22 and a position shifted by 90 ° from the minimum width portion 22a on the opposite side to the rotation direction R1. As it goes in the direction R1, it gradually expands toward the rotation axis A1. In other words, the dimension of the enlarged portion 28 in the radial direction is gradually increased toward the fan rotation direction R1.

Thereby, since the area of the enlarged portion 28 increases as the amount of air flowing through the air passage 22 increases, the backflow of the air blown out from the fan 12 is effectively suppressed, and interference with other blown winds is effectively prevented. Can be suppressed. Therefore, fan efficiency can be improved effectively.

In this embodiment, the evaporator 26 is arrange | positioned at the blower outlet 23. FIG. That is, since the blower 11 of the air conditioner is constituted by a centrifugal blower that does not have a scroll casing, the size of the air conditioner is reduced compared to the case where the blower 11 is provided with a scroll casing, and heat exchange is performed. The wind speed distribution in the vessel can be suppressed. Moreover, since there is no scroll casing, design and manufacture can be facilitated.
(Second Embodiment)
In the first embodiment, the enlargement portion 28 gradually expands toward the rotation axis A1 as it goes from the starting point portion 27 toward the fan rotation direction R1, but as shown in FIG. 8, the enlargement portion 28 has the rotation axis A1. The expansion dimension toward the front may be constant over the entire circumference of the air passage 22. In other words, the dimension of the enlarged portion 28 in the radial direction may be constant over the entire circumference of the air passage 22.
(Third embodiment)
In the second embodiment, the enlarged portion 28 is formed so as to be located radially outside of the fan 12 when viewed from the fan axial direction. However, as shown in FIG. You may form so that it may overlap with the fan 12 when it sees from an axial direction.
(Fourth embodiment)
In the above-described embodiment, the enlarged portion 28 is expanded downward on the lower side of the fan 12 (opposite the suction port 16). The enlarged portion 28 of the present embodiment is enlarged in the axial direction on both sides of the fan 12 in the axial direction. Specifically, as shown in FIG. 10, the air passage 22 has an enlarged portion 28 (enlarged portion 28 a) that expands downward on the lower side of the fan 12, and an upper side (on the inlet 16 side) of the fan 12. It has the expansion part 28 (expansion part 28b) expanded toward upper direction. In the example of FIG. 10, the enlarged portion 28 b overlaps the fan 12 when viewed from the axial direction of the fan 12.

In this embodiment, it has the

expansion parts

28a and 28b which expand in one (lower side) and the other (upper side) in the axial direction of the fan 12. Thereby, the air blown out from the fan 12 swirls at both the

enlarged portions

28a and 28b. Therefore, the backflow of the air blown out from the fan 12 is further suppressed, and interference with other blown winds can be further suppressed. Therefore, fan efficiency can be further improved.
(Fifth embodiment)
In the fourth embodiment, the enlarged portion 28 b is formed so as to overlap the fan 12 when viewed from the axial direction of the fan 12. In the present embodiment, as shown in FIG. 11, the enlarged portion 28 b does not overlap the fan 12 when viewed from the axial direction of the fan 12, and is formed on the outer side in the radial direction than the fan 12.

A portion of the blower casing 14 between the suction port 16 and the enlarged portion 28 b has a shape along the upper edge portion of the blade 121 of the fan 12. According to this, since the gap between the fan 12 and the blower casing 14 can be narrowed, the air blown out from the fan 12 to the air passage 22 can flow back to the suction port 16 side through the gap between the blade 121 and the blower casing 14. Can be prevented.
(Sixth embodiment)
In the above embodiment, one fan 12 is provided, but in this embodiment, two fans 12 are provided as shown in FIG.

The two fans 12 are arranged on opposite sides of the motor 13. The suction port 16 is formed on both ends of the blower casing 14 in the axial direction (the upper side and the lower side in FIG. 12).

The inside / outside air switching box (not shown) is connected to one suction port 16. The other suction port 16 is connected to a duct (not shown) extending from the inside / outside air switching box. The duct forms an air passage from the inside / outside air switching box to the other inlet 16. Thereby, the inside air and the outside air introduced from the inside / outside air switching box 20 are blown by the two fans 12.

The enlarged portion 28a is enlarged downward on one side of the fan 12 (downward in FIG. 12). The enlarged portion 28b is enlarged upward on the other side of the fan 12 (upper side in FIG. 12). According to this, interference with the other blown air can be reduced for both the air blown from one fan 12 and the air blown from the other fan 12. Therefore, fan efficiency can be improved.
(Seventh embodiment)
In the above embodiment, the inside air and the outside air introduced from the inside / outside air switching box 20 are blown by the two fans 12. On the other hand, in this embodiment, as shown in FIG. 13, outside air is blown by one fan 12 (fan 12b), and inside air is blown by the other fan 12 (fan 12a).

Outside air is introduced into one suction port (suction port 16b), and inside air is introduced into the other suction port (suction port 16a). A partition wall 30 is formed inside the blower casing 14. The partition wall 30 partitions the air passage 22 into an outside air passage 31 and an inside air passage 32. The outside air passage 31 is a passage through which outside air blown by the fan 12b flows. The inside air passage 32 is a passage through which the inside air blown by the fan 12a flows.

The outside air passage 31 has an enlarged portion 28 b and the inside air passage 32 has an enlarged portion 28. Thereby, interference with other blowing air can be reduced for both the outside air flowing through the outside air passage 31 and the inside air flowing through the inside air passage 32. Therefore, fan efficiency can be improved in the inside / outside air two-layer blower that blows the inside air and the outside air separately.
(Eighth embodiment)
14 to 17 are diagrams for explaining the relationship between the distance X1 between the fan 12 and the evaporator 26 and the air flow state in the eighth embodiment. In the present embodiment, the enlarged portion 28 is not formed in the air passage 22.

14 and 15, the two-dot chain line arrow indicates the air flow toward the evaporator 26. As shown in FIG. 15, when the distance X 1 between the fan 12 and the evaporator 26 is large, a vortex is easily generated in the air flow between the fan 12 and the evaporator 26.

On the other hand, as shown in FIG. 15, when the distance X1 between the fan 12 and the evaporator 26 is small, vortices are less likely to be generated in the air flow between the fan 12 and the evaporator 26. In other words, it flows into the evaporator 26 before the vortex is generated.

Therefore, as shown in FIG. 16, the smaller the distance X1 between the fan 12 and the evaporator 26, the higher the fan efficiency. In FIG. 16, a two-dot chain line indicates a comparative example. In the comparative example, the fan is a sirocco fan having the same diameter as that of the present embodiment, and the blower casing is a scroll casing having a nose.

In the comparative example, contrary to the present embodiment, the fan efficiency improves as the distance between the fan and the evaporator increases. Therefore, when the distance X1 between the fan and the evaporator is small, the fan efficiency of the present embodiment is higher than the fan efficiency of the comparative example.

FIG. 17 is a graph showing the relationship between the distance between the fan 12 and the evaporator 26 and the wind speed distribution in the evaporator 26. The vertical axis in FIG. 17 represents the standard deviation of the average wind speed measured for each of the divided parts by dividing the air inflow surface of the evaporator 26 into a large number (for example, 16 parts). In FIG. 16, the two-dot chain line indicates the comparative example.

As shown in FIG. 17, in this embodiment, even if the distance between the fan 12 and the evaporator 26 is small as compared with the comparative example, the deterioration of the wind speed distribution in the evaporator 26 can be suppressed.

In the present embodiment, the enlarged portion 28 is not formed in the air passage 22, but even if the enlarged portion 28 is formed in the air passage 22, the above-described operational effects of the present embodiment can be achieved.
(Ninth embodiment)
In the present embodiment, as shown in FIG. 18, a guide member 40 that guides the flow of air toward the evaporator 26 is disposed in a portion of the air passage 22 between the fan 12 and the outlet 23.

The guide member 40 may be integrally formed with the blower casing 14 or may be formed separately from the blower casing 14 and fixed to the blower casing 14 by screwing or the like.

The guide member 40 is formed in a plate shape that follows the flow of air toward the evaporator 26. Thereby, since the flow of the air which goes to the evaporator 26 is rectified by the guide member 40 and generation | occurrence | production of a vortex is suppressed, the wind speed distribution in the evaporator 26 can be suppressed.
(Other embodiments)
The above embodiments can be combined as appropriate. The above embodiment can be variously modified as follows, for example.

(1) In the above embodiment, the rotation axis A1 of the fan 12 is offset with respect to the center line CL of the blower casing 14 in the radial direction. However, the rotation axis A1 of the fan 12 may be disposed on the center line CL.

(2) In the above embodiment, the blower 11 blows out air in one direction from the outlet 23. However, the blower 11 may blow out air in a plurality of directions. For example, the blower 11 may blow out air radially from a large number of outlets.

(3) In the above embodiment, the air passage 22 is not provided with a nose. However, similar to the prior art of Patent Document 1, the air passage 22 may be provided with a protrusion (projection) that forms a nose.

(4) In the above embodiment, the indoor air-conditioning unit 10 constitutes a front-seat air-conditioning unit that blows conditioned air toward the passengers who are mainly seated in the front seat of the vehicle. However, the indoor air-conditioning unit 10 may constitute a rear-seat air-conditioning unit that blows conditioned air toward the passengers who are mainly seated in the rear seats of the vehicle. The indoor air conditioning unit 10 may constitute a seat air conditioner that blows conditioned air toward the passenger from the inside of the seat.

Claims

A turbofan (12) having a plurality of blades (121);
A casing (14) for accommodating the turbofan (12),
A radially outer portion of the turbofan (12) in the casing (14) forms a fluid passage (22) through which the fluid blown out from the turbofan (12) flows.
An outlet (23) for blowing out the fluid that has flowed through the fluid passage (22) is formed at an end of the casing (14) in the radial direction of the turbofan (12),
The dimension (W1) of the portion between the turbo fan (12) and the outlet (23) in the fluid passage (22) is larger than the diameter (d1) of the turbo fan (12). ,
The fluid passage (22) has an enlarged portion (28) that extends in the axial direction on at least one side of the axial direction from the turbo fan (12),
The expansion section (28) is a centrifugal blower that is a space in which air blown from the turbo fan (12) is swirled.
The enlarged portion (28) includes a first imaginary line (L1) extending from a rotation axis (A1) of the turbofan (12) toward the opening direction of the outlet (23), and the first imaginary line (L1). ) With the second imaginary line (L2) rotated 90 degrees in the rotation direction (R1) of the turbofan (12) around the rotation axis (A1) as a starting point, The centrifugal blower according to claim 1, wherein the centrifugal blower gradually expands toward the rotation axis (A1) as it goes toward the rotation direction (R1).
The fluid passage (22) has a minimum width portion (22a) in which the dimension of the fluid passage (22) in the radial direction is minimized,
The enlarged portion (28) is located between the minimum width portion (22a) and a position shifted from the minimum width portion (22a) by 90 ° on the opposite side to the rotation direction (R1) (27). The centrifugal blower according to claim 1, wherein the centrifugal fan gradually expands toward the rotation axis (A1) as it goes toward the rotation direction (R1) of the turbofan (12).
The centrifugal blower according to claim 1, wherein the dimension of the enlarged portion (28) in the radial direction is constant over the entire circumference of the fluid passage (22).
The centrifugal blower according to any one of claims 1 to 4, wherein the enlarged portion (28) overlaps with the turbo fan (12) when viewed from the axial direction.
The centrifugal blower according to any one of claims 1 to 5, wherein the expansion portion (28) extends in the axial direction on both sides in the axial direction of the turbofan (12).
A blower (11) for blowing air;
A heat exchanger (26) for exchanging heat of the air blown by the blower (11),
The blower (11) is a centrifugal blower having a turbo fan (12) including a plurality of blades (121) and a casing (14) for housing the turbo fan (12),
A radially outer portion of the turbofan (12) in the casing (14) forms a fluid passage (22) through which the fluid blown out from the turbofan (12) flows.
An outlet (23) for blowing out the fluid that has flowed through the fluid passage (22) is formed at an end of the casing (14) in the radial direction of the turbofan (12),
The dimension (W1) of the portion between the turbo fan (12) and the outlet (23) in the fluid passage (22) is larger than the diameter (d1) of the turbo fan (12). ,
An air conditioner in which the heat exchanger (26) is disposed at the air outlet (23).
A guide member (40) for guiding the flow of the fluid toward the heat exchanger (26) is provided in a portion of the fluid passage (22) between the turbofan (12) and the outlet (23). The air conditioner according to claim 7 in which is arranged.